Mitsubishi Y04-003 DATA BOOK

 

Outdoor-Air Processing unit

GUF-50/100RD3 GUF-50/100RDH3

CHAPTER 1 Product Section

1. Summary .......................................................................................................................................... 2

2. Main Functions of OA Processing Unit.............................................................................................. 3

3. Model Line-Up .................................................................................................................................. 4

4. Summary of Types ............................................................................................................................ 4

5. Specifications .................................................................................................................................... 5

6. Outline Drawings .............................................................................................................................. 7

7. Electric Wiring Diagrams .................................................................................................................. 8

8. Characteristic Curves ........................................................................................................................ 10

9. Construction and Principle of Heat Recovery Unit (Lossnay Core) .................................................. 11

10. Total Heat Recovery Characteristics ................................................................................................ 13

11. Principle and Features of Permeable Film Humidifier ...................................................................... 14

12. Cooling and Heating Characteristics ................................................................................................ 18

13. Filter Characteristics.......................................................................................................................... 33

14. Noise Characteristics ........................................................................................................................ 35

15. Reference Documents ...................................................................................................................... 36

CHAPTER 2 Air Conditioning System Design Section

1. Guide to a Comfortable Air Conditioning System.............................................................................. 48

2. Features of the OA Processing Unit.................................................................................................. 49

3. Air Conditioning and Ventilation ........................................................................................................ 50

4. Characteristics .................................................................................................................................. 61

5. Lossnay Core Effect .......................................................................................................................... 64

6. Humidifying........................................................................................................................................ 70

7. Humidifying Effect of the OA Processing Unit ..................................................................................72

8. Water Quality and Service Life of Humidifier .................................................................................... 75

9. Dust Removal.................................................................................................................................... 77

10. Sound ................................................................................................................................................ 82

11. Precautions when Using.................................................................................................................... 87

CHAPTER 3 Control System Design Section

1. System Selection .............................................................................................................................. 92

2. Precautions when Designing Systems .............................................................................................. 99

3. Cable Installation .............................................................................................................................. 100

4. System Designs ................................................................................................................................ 104

5. Control of OA Processing Unit .......................................................................................................... 106

6. Automatic Ventilation Switching ........................................................................................................ 107

7. Operation with Cooling/Heating ........................................................................................................ 110

8. Feature Settings ................................................................................................................................ 115

9. How to Operate ................................................................................................................................ 120

10. System Component .......................................................................................................................... 126

11.Troubleshooting ................................................................................................................................ 129

12. Remote Controller Check Code List.................................................................................................. 130

13. Circuit Test Point................................................................................................................................ 131

CHAPTER 1

Product Section

CHAPTER 1 ● Product Section

1. Summary

Introducing state-of-the-art comprehensive air conditioning that provides precise control for individual rooms.

RDH3 series : Lossnay Ventilation and efficient humiditying. RD3 series : Lossnay Ventilation and the Air conditioner.

(1)When the load is light. → Main Air conditioner. (2)When the load is heavy. → Supplemental Air conditioner.

Introducing the latest advancement for total air conditioning comfort – the Outdoor Air processing unit (hereafter OA processing unit). It uses the latest technology to provide comprehensive air conditioning control including ventilation, heat recovery, humidifying, heat processing and dust removal*. Control can be performed for each room, giving the flexibility to create the best comfort for each type of living space.

Note: (Dust removal) ......This function is enabled by using the optional high-efficiency filter.

The exhaust fan

High-efficiency filters (Option)

The supply fan

Maintenance cover

EA (Exhaust air)

The heat of room air is recovered (sensible and latent heat) by Lossnay Core, and exhausted to the outside of the room by the exhaust fan.

OA (Outdoor air)

Fresh outdoor air in a quantity corresponding to the required ventilation rare is taken in by the supply fan.

Lossnay Core

Temperature and humidity are recovered between supply air and exhaust air.

Air filter

Prevents clogs in the Lossnay Core.

Direct Expansion coil

The outdoor air taken in is cooled or heated by Direct Expansion coil.

Permeable-film humidifier

Outdoor air taken in is humidified by the permeable film humidifier as required for more comfortable air conditioning. Not available on GUF-50/100RD3.

SA (Supply air)

The fresh outdoor air processed is supplied to the inside of rooms.

RA (Return air)

Contaminated room air is sucked by the exhaust fan.

CHAPTER 1 ● Product Section

2. Main Functions of OA Processing Unit

2.1 Common Functions of Humidifying/Non-Humidifying Type (GUF-RDH3/RD3)

●

Ventilation

Ensures proper ventilation by simultaneous forced air induction and exhaust.

Dual intake fans are used to simultaneously force both supply air diffuser and exhaust. This means that even sealed buildings will be ensured of proper ventilation.

●

Heat recovery

Heat recovery system that provides energy-saving operation.

The unit has a built-in static type total heat recovery unit Lossnay Core. There is no mixing of the intake and exhaust air as they pass through the Lossnay Core. Recover of both temperature (sensible heat) and humidity (latent heat) – in other words total heat recovery – is performed with minimal loss to the heating or cooling effect, ensuring energy-saving operation.

●

Dust removal*

High-efficiency filter provides 65% filtration using colorimetric method (Optional parts)

The high-efficiency filter provides up to 3,000 hours of maintenance free operation and is capable of 65% filtration (colorimetric method). It can be installed inside of the OA processing unit itself, so no additional installation space is required. In addition, the high-efficiency filter can be installed after the OA processing unit has been installed. Note: This function is enabled by using the optional high-efficiency filter.

●

Free Cooling

When the air conditioning system is operating in its cooling mode and the temperature of the air outdoors drops below the temperature indoors (e.g.a summer night), the OA processing unit detects this and automatically switches to a mode of operation which bypasses the heat-exchange element. Bringing in cool air from outside serves to help reduce the air conditioner’s cooling load.

2.2 Functions of Humidifying Type (GUF-RDH3)

●

Humidifier

Total introduction of permeable-film humidifier that functions using natural evaporation.

The humidifier installed in the OA processing unit was designed exclusively by Mitsubishi Electric. It is the permeable-film humidifier that functions using natural evaporation. This design total eliminates the spreading of impurities such as breaching powder and silicon dioxide. This means that this system can provide a clean supply air diffuser free of white exhaust.

●

Heat processing

Efficient heat processing and compact design allows for design freedom.

By including the direct expansion coil, approximately 25% of the air conditioning load can be heat processed by the OA processing unit. This means that the air conditioning unit itself can be more compact. And since it totally processes the outdoor air loads, it is possible to separate outdoor air loads and indoor air loads, allowing the freedom for easier installation designs. In addition, air passes through the permeable film humidifier that increases its heat and ensures proper humidity content.

2.3 Functions of Non-Humidifying Type (GUF-RD3)

●

Air conditioning

The high-performance direct-expansion coil and the air conditioning and Lossnay Core allow a single OA processing unit to provide low-energy heating and cooling ventilation.

Model 50

Rated air flow volume

500 m3/h

CHAPTER 1 ● Product Section

3. Model Line-Up

4. Summary of Types

Outdoor Air processing unit

H: with humidifier

D: with direct-expansion coil

R: Ceiling recessed

Air volume 50: 500 m

100:1,000 m3/h

GUF

–

50 R D H

Humidifying type Direct-expansion coil and permeable-film humidifier

Non-humidifying type

Direct-expansion coil

Model 100

Rated air flow volume

1,000 m3/h

Ventilation, Heat recovery,

Humidifying, Heat processing

and (Dust removal)

Ventilation, Heat recovery,

Air conditioning and

(Dust removal)

GUF-50RD3

Ventilation, Heat recovery,

Humidifying, Heat processing

and (Dust removal)

GUF-100RDH3

Ventilation, Heat recovery and

(Dust removal)

GUF-100RD3

Note: (Dust removal) ......This function is enabled by using the optional high-efficiency filter.

GUF-50RDH3

3: Development Version

GUF-50RDH3 GUF-100RDH3

Lossnay ventilation By-pass ventilation Lossnay ventilation By-pass ventila

tion

High Low High Low High Low High Low

Single phase 220 V - 240 V 50 Hz Single phase 220 V - 240 V 50 Hz

1.15 0.70 1.15 0.70 2.20 1.76 2.25 1.77

235-265 150-165 235-265 150-165 480-505 385-400 490-515 385-410

(P)32 (P)63

5.29 (DX coil:3.63, Lossnay:1.66) 10.81 (DX coil:7.32, Lossnay:3.49)

6.42 (DX coil:4.17, Lossnay:2.25) 13.00 (DX coil:8.30, Lossnay:4.70)

2.7 (heating) 5.4 (heating)

Supply air: Centrifugal fan [Sirocco fan] × 1 Exhaust air: Centrifugal fan [Sirocco fan] × 1

500 400 500 400 1,000 800 1,000 800 125 80 125 80 135 86 135 86

Totally enclosed capacitor permanent split-phase induction motor, 4 poles, 2 units

33.5-34.5 29.5-30.5 35-36 29.5-30.5 38-39 34-35 38-39 35-36 317 398

1,016 1,231 1,288 1,580

57 (filled with water 61) 98 (filled with water 106)

LEV control

12.7 15.88

6.35 9.52 VP25

Permeable film humidifier

Minimum pressure: 2.0 × 10

Pa Maximum pressure: 49.0 × 104Pa

R1/2 of External thread

Non-woven fabrics filter: Gravitational method 82%

High-efficiency filter: Colorimetric method 65% (optional parts)

Non-woven fabrics filter: Gravitational method 82%

CHAPTER 1 ● Product Section

5. Specifications

5.1 Humidifying Type

Fan

Lossnay Core Direct Expansion coil Humidifier

High-efficiency filter (Optional parts)

Air filter

Ventilation

Heat

recovery

Humidifying

Heat

processing

(

Dust removal

Model

Items

Power source Current Input Capacity equivalent to the indoor unit Cooling capacity Heating capacity Humidifying capacity

Fan

Fan motor Noise level

Maximum dimensions

Weight Refrigerant control Refrigerant pipe dimensions Drain pipe dimension Type of humidifier Water supply pressure Water supply pipe dimension

Filter

Width

Height

Depth

Gas

Liquid

kW kW

kg/h

dB (A)

mm mm mm

ø mm ø mm

Note: (Dust removal) ......This function is enabled by using the optional high-efficiency filter.

Supply air

Type × No. of fans

Air volume

External static pressure

Exhaust air

CHAPTER 1 ● Product Section

GUF-50RD3 GUF-100RD3

Lossnay ventilation By-pass ventilation Lossnay ventilation By-pass ventilation

High Low High Low High Low High Low

Single phase 220 V - 240 V 50 Hz Single phase 220 V - 240 V 50 Hz

1.15 0.70 1.15 0.70 2.20 1.73 2.25 1.77

235-265 150-165 235-265 150-165 480-505 370-395 490-515 385-410

(P)32 (P)63

5.29 (DX coil:3.63, Lossnay:1.66) 10.81 (DX coil:7.32, Lossnay:3.49)

6.42 (DX coil:4.17, Lossnay:2.25) 13.00 (DX coil:8.30, Lossnay:4.70)

Supply air diffuser: Centrifugal fan [Sirocco fan] × 1 Exhaust air: Centrifugal fan [Sirocco fan] × 1

500 400 500 400 1,000 800 1,000 800 140 90 140 90 140 90 140 90

Totally enclosed capacitor permanent split-phase induction motor, 4 poles, 2 units

33.5-34.5 29.5-30.5

35-36

29.5-30.5 38-39 34-35

38-39

35-36

317 398 1,016 1,231 1,288 1,580

54 92

LEV control

12.7 15.88

6.35 9.52 VP25

Non-woven fabrics filter: Gravitational method 82%

High-efficiency filter: Colorimetric method 65% (optional parts)

Non-woven fabrics filter: Gravitational method 82%

5.2 Non-Humidifying Type

Ventilation

Heat

recovery

Air

conditioning

(

Dust removal

Model

Items

Power source Current Input Capacity equivalent to the indoor unit Cooling capacity Heating capacity

Fan

Fan motor Noise level

Maximum dimensions

Weight Refrigerant control Refrigerant pipe dimensions Drain pipe dimension

Filter

Width

Height

Depth

Gas

Liquid

kW kW

dB(A)

mm mm mm

ø mm ø mm

Note: (Dust removal) ......This function is enabled by using the optional high-efficiency filter.

Supply air

Type × No. of fans

Exhaust air

Fan

Lossnay Core Direct Expansion coil

High-efficiency filter (Optional parts)

Air filter

Air volume

External static pressure

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CHAPTER 1 ● Product Section

6. Outline Drawings

6.1 Humidifying Type GUF-50/100RDH3

6.2 Non-Humidifying Type GUF-50/100RD3

Unit (mm)

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Unit (mm)

Model A

GUF-50RDH3

745

1,016

124

1,185

1,048 22 124 450 372.5 435 158.5

GUF-100RDH3

920

1,231

149

1,465

1,271 16 149 600 460 670 199

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Model M

GUF-50RDH3

317

1,288

124 266 192 208 12.7 6.35 347 99 135

GUF-100RDH3

398

1,580

149 280 242 258 15.88 9.52 361 110 169

NPQRSTUVWX

Model A

GUF-50RD3

745

1,016

124

1,185

1,048 22 124 450 372.5 435 158.5

GUF-100RD3

920

1,231

149

1,465

1,271 16 149 600 460 670 199

BCDEFGHJ KL

Model M

GUF-50RD3

317

1,288

124 266 192 208 12.7 6.35 347 135

GUF-100RD3

398

1,580

149 280 242 258 15.88 9.52 361 169

NPQRSTUVW

LED3

SW4

SW5

BROWN

BLUE

RED

BLUE

BROWN

/ YELLOW

PURPLE

FAN1

FAN4

CN3TCNT

CND1 CND2

GREEN

BLACK

YELLOW YELLOW

TH4 (RA)

TH1 (OA)

YELLOW

WHITE

RED

PINK

YELLOW

GREY

YELLOW

ORANGE

RED

WHITE WHITE ORANGE

PURPLE

ORANGE

BLUE

WHITE

RED

BLACK

PINK

GREEN/ YELLOW

BLACK

PINK

ORANGE

WHITE

RED

GREEN/ YELLOW

CN22

CN29

CN21

SW1

SW2

SW3

SW12

LED1

LED2

SW11

SW14

CN20

SV1

SV2

L S

W. S

RED

PURPLE

BROWN

RED

PURPLE

ORANGE

PINK

WHITE

CN60

CN70

CNL

CN27

CN4D

RED

FAN2

FAN3

FUSE1

PAR-F27MEA

PAR-20MAA

Remote Controller

Uncharged a-contact

Humidistat

240VAC more than 10mA

Operation monitor output

AC240V 1A AC220V 100mA DC 24V 1A DC 5V 100mA

MAX MIN

Malfunction monitor output MAX MIN AC240V 1A AC220V 100mA DC 24V 1A DC 5V 100mA

Shield wire

M-NET Remote controller

Fresh Master

To Outdoor Unit , BC Controller

X09

X08

M-NET transmissiion cable

DB901

ZNR901ZNR902

DSA1

X05

X04

X07

X06

X03

X02

BREAKER (16A)

RSV (1kΩ)

pipe

Liquid

TH2

pipe

Gas

TH3

SUPPLY FAN

EXHAUST FAN

PINK

TM2

TM3

TM1

LEV

220-240V ~50Hz

POWER SUPPLY

MARK : indicates terminal block, : connector

: board insertion connector or fastening connector of control board.

Symbol Explanation

M1 M2 C W. S SV1 SV2 TH1 TH2 TH3 TH4 LEV RSV

Fan motor (exhaust) Fan motor (supply) Capacitor Water sensor Solenoid valve (pressure regulator) Solenoid valve (exhaust) Thermistor (outdoor air temp. detection) Thermistor (pipe temp. detection/liquid) Thermistor (pipe temp. detection/gas) Thermistor (room air temp. detection) Electronic linear expansion valve Resistance (solenoid valve)

TM1 TM2 TM3 SW1 SW2 SW3 SW4 SW5 SW11 SW12 SW14

Terminal block (power supply) Terminal block (transmission) Terminal block (humidistat, monitor) Switch (function selection) Switch (capacity code setting) Switch (function selection) Switch Switch Switch (1st digit address set) Switch (2nd digit address set) Switch (branch NO. set)

1, 2 A, B S CND1, CND2 X02-X09 TR GM LS LED1 LED2

LED3

Remote controller terminal M-NET transmission terminal Shield Connector (power supply) Relay Transformer Damper motor Limit switch Power supply monitor MA remote controller Power supply monitor M-NET Power supply monitor

Symbol Name Symbol Name Symbol Name

250V 6.3A

CHAPTER 1 ● Product Section

7. Electric Wiring Diagrams

7.1 Humidifying Type GUF-50/100RDH3

●

TM1, TM2, TM3 shown in dotted lines are field work.

●

Be sure to connect the grounding wire.

●

Breakers and controller switches should be provided by the customer.

CHAPTER 1 ● Product Section

7.2 Non-Humidifying Type GUF-50/100RD3

●

TM1, TM2 shown in dotted lines are field work.

●

Be sure to connect the grounding wire.

●

Breakers and controller switches should be provided by the customer.

Symbol Explanation

M1 M2 C W.S TH1 TH2 TH3 TH4 LEV

Fan motor (exhaust

) Fan motor (supply) Capacitor Water sensor Thermistor (outdoor air temp. detection

) Thermistor (pipe temp. detection/liquid) Thermistor (pipe temp. detection/gas) Thermistor (room air temp. detection

)

Electronic linear expansion valve

TM1 TM2 TM3 SW1 SW2 SW3 SW4 SW5 SW11 SW12 SW14

1, 2 A, B S CND1, CND2 X02-X09 TR GM LS LED1 LED2

LED3

Symbol Name Symbol Name Symbol Name

PINK

FUSE1

PAR-F27MEA

PAR-20MAA

Remote Controller

Operation monitor output

AC240V 1A AC220V 100mA DC 24V 1A DC 5V 100mA

MAX MIN

Malfunction monitor output MAX MIN AC240V 1A AC220V 100mA DC 24V 1A DC 5V 100mA

Shield wire

M-NET Remote controller

Fresh Master

To Outdoor Unit , BC Controller

X09

X08

M-NET transmission cable

DB901

ZNR901

ZNR902

DSA1

X05

X04

X07

X06

X03

X02

BREAKER (16A)

220-240V ~50Hz

POWER SUPPLY

pipe

Liquid

TH2

pipe

Gas

TH3

SUPPLY FAN

EXHAUST FAN

MARK : indicates terminal block, : connector

: board insertion connector or fastening connector of control board.

LED3

SW4

SW5

BROWN

BLUE

RED

BLUE

BROWN

/YELLOW

PURPLE

FAN1

FAN4

CN3TCNT

CND1 CND2

GREEN

BLACK

YELLOW YELLOW

TH4 (RA)

TH1 (OA)

YELLOW

WHITE

RED

PINK

YELLOW

GREY

YELLOW

ORANGE

RED

WHITE WHITE ORANGE

PURPLE

ORANGE

BLUE

WHITE

RED

BLACK

PINK

GREEN/ YELLOW

BLACK

PINK

ORANGE

WHITE

RED

GREEN/ YELLOW

CN22

CN29

CN21

SW1

SW2

SW3

SW12

LED1

LED2

SW11

SW14

CN20

L S

W. S

BROWN

RED

PURPLE

ORANGE

PINK

WHITE

LEV

CN60

CN70

CNL

CN27

CN4D

FAN2

FAN3

TM3

TM1

TM2

250V 6.3A

CHAPTER 1 ● Product Section

8. Characteristic Curves

8.1 Humidifying Type

8.2 Non-Humidifying Type

Low

High

Enthalpy exchange

efficiency (Cooling)

Enthalpy exchange

efficiency (Heating)

Temperature exchange

efficiency

300

(Pa)

External static pressure

Exchange efficiency

500

200

400

Air volume (L/s)

35025020015010050 3000

1400

/h)

12001000800600400200

100m

80m

60m

40m

20m

250mm dia pipe length

100

(%)

Low

High

Enthalpy exchange

efficiency (Cooling)

Enthalpy exchange

efficiency (Heating)

Temperature exchange

efficiency

020 220180 2006040 80 100 120 140 160

Air volume (L/s)

/h)

200mm dia pipe length

(Pa)

External static pressure

Exchange efficiency

m06

001

m04

m02

m08

060040020 080

(%)

GUF-100RDH3GUF-50RDH3

Low

High

Enthalpy exchange

efficiency (Cooling)

Enthalpy exchange

efficiency (Heating)

Temperature exchange

efficiency

300

(Pa)

External static pressure

Exchange efficiency

500

100

200

400

Air volume (L/s)

35025020015010050 3000

1400

/h)

12001000800600400200

100m

80m

60m

40m

20m

pipe length

250mm dia.

(%)

Low

High

Enthalpy exchange

efficiency (Cooling)

Enthalpy exchange

efficiency (Heating)

Temperature exchange

efficiency

Air volume (L/s)

220160140120100802004060 200180

/h)

060

External static pressure

(Pa)

Exchange efficiency

080020 040

80m

20m

40m

100

60m

pipe length

200mm dia.

(%)

GUF-100RD3GUF-50RD3

CHAPTER 1 ● Product Section

9. Construction and Principle of Heat Recovery Unit (Lossnay Core)

●

Simple construction

The Lossnay Core is a cross-flow total heat recovery unit constructed of plates and fins made of treated paper. The fresh air and exhaust air passages are completely separated allowing the fresh air to be introduced without mixing with the exhaust air.

●

Principle

The Lossnay Core uses the heat transfer properties and moisture permeability of the treated paper. Total heat (sensible heat plus latent heat) is transferred from the stale exhaust air to the fresh air being introduced into the system when they pass through the Lossnay Core. Try this simple experiment. Roll a piece of paper into a tube and blow through it. Your hand holding the paper will immediately feel warm. If cold air is blown through the tube, your hand will immediately feel cool. This means heat is transferred through paper. Lossnay Core is a total heat recovery unit that utilizes these special properties of paper.

●

Treated paper

The paper partition plates are specially treated so that the Lossnay Core is an appropriate heat recovery unit for the ventilator. This paper differs from ordinary paper, and has the following unique properties.

(1) The paper is incombustible and is strong.

(2) The paper has selective hydroscopicity and moisture permeability that permits the passage of water vapor

only (including some water-soluble gases).

(3) The paper has gas barrier properties that does not pass gases such as CO

A comparison of the ordinary paper and the Lossnay Core plates is as shown in the table.

Ordinary paper

Water vapor is transferred, but gas elements that are easily dissolved in water such as CO2, NO2 are also transferred.

The contaminated air passes through the plates during ventilation and returns to the room.

Treated paper

Water vapor is transferred, but gas elements such as CO

2, NO2

are not transferred.

The contaminated air does not return to the room when ventilated.

SA Supply air diffuser (Fresh cold or warm air)

Partition plate (Treated paper)

Spacer plate (Treated paper)

RA Return air (Stale cold or warm air)

Indoors Outdoors

EA Exhaust air (Stale air)

OA Outdoor air (Fresh air)

Highly humid air

Water vapor

2 NO2

CO2 NO2

CO2 NO2Water vapor

Water vapor

Treatment (Selective permeable film) (Incombustible specifications)

Low humid air

Highly humid air

Cellulose fibers

Low humid air

CHAPTER 1 ● Product Section

●

Total heat recovery mechanism

Sensible heat and latent heat

The heat that enters and leaves in accordance with changing temperature (rise or drop) is called sensible heat. The heat that enters and leaves due to the changes in the physical properties of the matter (evaporation, condensation) is called latent heat.

(1) Heat (sensible heat) exchange

1) Heat conduction and heat passage is performed through a partition plate from the high temperature to low temperature side.

2) As shown on the right, the heat exchange efficiency is affected by the resistance of the boundary layer, and for the Lossnay Core there is little difference when compared to materials such as copper or aluminium which also have high thermal conductivity.

Heat resistance coefficients

Treated paper Cu Al

Ra1 10 10 10

Rp 1 0.00036 0.0006

Ra2 10 10 10

Total 21 20.00036 20.0006

(2) Humidity (latent heat) exchange

●

Water vapor is moved through the partition plate from the high humidity to the low humidity side by means of the differential pressure in the vapor.

Ra1

Ra2

Partition plate Ra1+Ra2

»Rp

High humidity side

Low humidity side

Partition plate

CHAPTER 1 ● Product Section

10. Total Heat Recovery Characteristics

10.1 Lossnay Core Heat Recovery Characteristic

50 60 70 80 90 100

Exchange efficiency (%)

800

200 400 600

Exchange efficiency (%)

SA Air volume (m3/h)

1400120010008006004002000

50 60 70 80 90 100

Exchange efficiency (%)

SA Air volume (m3/h)

*Air volume ratio =

Exhaust air flow volume

Suplly air flow volume

●

Obtaining the efficiency when supply air and exhaust air volumes differ

The efficiency obtained from the intake side air volume in each characteristic curve can be corrected with the air volume ratio in the chart on the right. If the intake side and exhaust side duct lengths differ greatly or if a differential air volume is required, obtain the intake side efficiency from the chart on the right.

Efficiency when there is no air volume difference between exhaust side and supply side.

Efficiency of supply air flow after correction

Air volume ratio =

Exhaust air volume

Supply air volume

GUF-50RDH3/50RD3

GUF-100RDH3/100RD3

0.5 0.6 0.7 0.8 0.9 1.0 1.1 1.4

1.2 1.3

Exchange efficiency (%)

ηt : Heat exchange efficiency after correction (%)

0.5 0.6 0.7 0.8 0.9 1.01.1 1.4

1.2 1.3

Enthalpy exchange efficiency (Cooling) : ηic

Characteristics curve Enthalpy exchange efficiency (Heating) : ηiH

Temperature exchange efficiency : ηt

Enthalpy exchange efficiency (Cooling) : ηic

Characteristics curve Enthalpy exchange efficiency (Heating) : ηiH

Temperature exchange efficiency : ηt

Efficiency correction curve

← Air volume ratio*

CHAPTER 1 ● Product Section

11. Principle and Features of Permeable Film Humidifier

11.1 Principles and Construction of Permeable Film Humidifier

Basic

A permeable film type humidifier uses the basic characteristics of natural evaporation. In this model, those characteristics have been dramatically improved. The main points of the improvement are that the water is wrapped in an ultra-water-repellant porous film (the permeable film) that forms a surface for releasing the water vapor and that the surface are of this evaporating surface has been dramatically increased.

Principle

As shown in Fig. 1, there are tubes filled with water. Space is provided between these tubes for air to pass through, forming a “layered strip” design that ensures rectangular- shaped flow passages. Since the permeable film of the tube (ultra-water repellant porous film) allows water moisture to pass through in an evaporated state, the water in the tube is released from the surface of the tube in an evaporated state and is included with the passing air as shown in Fig. 1 (b). As can be seen by looking Fig. 2, spacers have been placed between the tubes of permeable film to form layered openings for air to pass through. This provides an extremely large humidifying surface area – 8.5 times larger than natural evaporation type humidifiers of the same size and offering an increase of humidifying performance that is 6 times greater.

Fig. 1 Principles behind permeable film humidifier Fig. 2 Humidifying module

Output air from Lossnay Core

Permeable film

Humidified air outlet

Water

Humidified air outlet

(a) Water cross section of layered humidifying section.

(b) Cross section of layered humidifying section.

Water supply by pressure

reduction solenoid valve

Water supply port

Humidifier element

CHAPTER 1 ● Product Section

Construction

1) The water supply unit is comprised of strainer, pressure reduction solenoid valve and supply pipe. This design ensures stable water pressure and water volume are supplied to the humidifier unit.

The strainer removes foreign material as water passes through the water supply piping. The solenoid valve opens to allow the water to be supplied while the pressure reduction valve ensures that water pressure is maintained at 7 kPa or less as water is supplied to the humidifier unit. (If the water pressure exceeds 7 kPa, the safety valve opens and the water is discharged to a drain.)

2) As explained in the operating principles for the humidifying unit, the tube-shaped permeable film is arranged in a layered construction and spacers have been provided to create opening for the air to pass through. Water is supplied to these tubes and then evaporates from their surfaces into the air.

Note that any impurities in the water settle to the bottom of the tube and, due to the extremely large surface area of the permeable film, have almost no affect on the creation of humidity.

Basic design of a permeable film humidifier

Spacer

Permeable film tube

Humidifier unit

Humidified air outlet

Supply air diffuser from Lossnay Core

Water supply piping

Pressure reduction solenoid valve

Drain port

Safety valve

Pressure reduction valve

Solenoid valve

Strainer

Water

CHAPTER 1 ● Product Section

11.2 Features of Permeable Film Humidifier

Design of the new type permeable film type humidifier

The previous type of permeable film had a selective-type permeable layer that only allowed water vapor to pass through surfaces in contact with water and base cloth with a layer of porous PTFE with extremely fine pores with 1/20,000 water droplets and 1,000 times water vapor (0.1 to 1 µm) that allowed evaporation without air or water passing through. The new type permeable film does not have the base cloth used in the previous permeable membrane. Instead, it has an ultra water-resistant porous permeable film that reduces the resistance to permeation by 1/2 when compared with the previous type and a 3-dimensional fabric that ensures water passages inside the permeable film tube, dramatically improving the ability for water vapor only to permeate.

●

New type permeable film type

●

New unit

●

3-dimensional fabric

The 3-dimensional fabric inside the new type of permeable film tube is comprised of spiral-like threads that are attached upright in the tube. These act as a type of reinforcing material for ensuring the passage of water inside the permeable film tubes. This 3-dimensional fabric used in the new type permeable film type humidifier keep the permeable film tubes from collapsing and ensure that the water supplied at a constant pressure from the water supply port at the base of the humidifier seeps to the ends of the humidifying surface.

Water

Selective-type permeable layer

PTFE layer

Base cloth

Water vapor

Air

Water

3-dimentional fabric

Water-resistant porous permeable film

Water vapor

Air

Permeaable film tube

3-dimentional fabric

Spacer

●

Previous permeable film

CHAPTER 1 ● Product Section

0246–6

5.8

5.6

5.4

5.2

4.8

4.6

4.4

4.2

–4 –2

RA 22°C40% RA 21°C40%

RA 21°C50%

RA 20°C40%

RA 20°C50%

RA 22°C50%

0246–6

2.9

2.8

2.7

2.6

2.5

2.4

2.3

2.2 –4 –2

RA 22°C40%

RA 21°C40%

RA 22°C50% RA 21°C50%

RA 20°C40%

RA 20°C50%

Reference

Quick reference graph for amount of humidifying

Conditions:

●

The air flow is the rated air flow (GUF-50RDH3: 500 m3/h GUF-100RDH3: 1,000 m3/h )

●

The connections to the outdoor unit are an OA processing unit and indoor unit for a total capacity of 100%.

●

The relative humidity of the outdoor air is 50%.

Amount of humidifying (kg/h)

Outdoor Air temperature (°C)

GUF-50RDH3

GUF-100RDH3

Amount of humidifying (kg/h)

Outdoor Air temperature (°C)

CHAPTER 1 ● Product Section

Note: When using a combination of City Multi and Air Multi units, there is a need to calculate the total value of

performance capacity of the indoor units connected to each outdoor unit as a parameter. This information can be found in the technical documentation for the units. Refer to the City Multi Data Book for details.

Dry bulb Wet bulb Relative

Enthalpy

temperature temperature humidity

Outdoor air 35°CDB 24°CWB 40% 71.6kJ/kg

Indoor air 27°CDB 19.5°CWB 50% 55.7kJ/kg

Heat exchange inlet air

50 28.8°CDB 21.3°CWB 51.7% 61.7kJ/kg

(Lossnay Core outlet temperature)

100 28.7°CDB 21.2°CWB 51.4% 61.2kJ/kg

Outdoor air 7°CDB 6°CWB 85% 20.5kJ/kg

Indoor air 21°CDB 14.6°CWB 50% 40.6kJ/kg

Heat exchange inlet air

50 17.8°CDB 12.0°CWB 49.9% 33.9kJ/kg

(Lossnay Core outlet temperature)

100 18.1°CDB 12.3°CWB 50.5% 34.7kJ/kg

CoolingHeating

Model number Model 50 Model 100

City Multi indoor unit equivalent 32 63

Cooling capacity 3.63kW 7.32kW

Heating capacity 4.17kW 8.30kW

12. Cooling and Heating Characteristics

12.1 Direct Expansion Coil Characteristics

12.1.1 Rated operating conditions <At rated air flow>

12.1.2 Standard cooling and heating performance

12.1.3 Cooling Capacity (In combination with PUHY, PURY)

GUF-50RD3

CA:Capacity (kW) SHC:Sensible heat capacity (kW)

21.5°CDB 15°CWB

23°CDB

16°CWB

25°CDB

18°CWB

27°CDB

19.5°CWB

28°CDB

20°CWB

30°CDB

22°CWB

32°CDB

24°CWB

20.0 12.0 3.3 2.0 3.4 2.1 3.4 2.1 3.5 2.1 3.6 2.2 3.7 2.3 3.8 2.3

22.5 14.0 3.3 2.0 3.4 2.1 3.5 2.1 3.6 2.2 3.6 2.2 3.7 2.3 3.8 2.3

25.0 16.0 3.3 2.0 3.4 2.1 3.5 2.1 3.5 2.1 3.6 2.2 3.8 2.3 3.8 2.3

27.5 18.0 3.3 2.0 3.4 2.1 3.5 2.1 3.5 2.1 3.6 2.3 3.7 2.2 3.8 2.2

30.0 20.0 3.4 2.1 3.4 2.1 3.5 2.1 3.5 2.1 3.6 2.2 3.7 2.2 3.8 2.2

32.5 22.0 3.4 2.0 3.4 2.0 3.4 2.1 3.5 2.1 3.7 2.2 3.7 2.2 3.8 2.2

35.0 24.0 3.3 1.9 3.4 2.0 3.4 2.1 3.6 2.2 3.6 2.2 3.7 2.1 3.8 2.2

37.5 26.0 3.3 1.9 3.4 2.0 3.4 2.1 3.6 2.1 3.6 2.1 3.7 2.1 3.7 2.1

40.0 28.0 3.3 1.9 3.3 1.9 3.5 2.0 3.6 2.1 3.5 2.0 3.7 2.1 3.7 2.1

43.0 30.0 3.3 1.9 3.3 1.9 3.5 2.0 3.6 2.0 3.5 1.9 3.6 2.0 3.6 2.0

WBRACA SHC CA SHC CA SHC CA SHC CA SHC CA SHC CA SHC

CHAPTER 1 ● Product Section

GUF-100RD3

CA:Capacity (kW) SHC:Sensible heat capacity (kW)

21.5°CDB 15°CWB

23°CDB

16°CWB

25°CDB

18°CWB

27°CDB

19.5°CWB

28°CDB

20°CWB

30°CDB

22°CWB

32°CDB

24°CWB

20.0 12.0 6.9 4.3 7.0 4.5 7.0 4.5 7.3 4.6 7.4 4.6 7.6 4.9 7.9 4.9

22.5 14.0 6.9 4.3 7.0 4.4 7.2 4.4 7.4 4.5 7.4 4.5 7.6 4.9 7.8 4.8

25.0 16.0 6.9 4.3 7.1 4.4 7.2 4.4 7.3 4.5 7.3 4.5 7.7 4.7 7.8 4.8

27.5 18.0 6.9 4.3 7.1 4.4 7.2 4.4 7.2 4.4 7.3 4.6 7.6 4.7 7.9 4.7

30.0 20.0 6.9 4.2 7.0 4.2 7.1 4.3 7.2 4.5 7.3 4.5 7.6 4.7 7.9 4.7

32.5 22.0 6.9 4.2 7.0 4.2 7.1 4.3 7.2 4.4 7.4 4.5 7.6 4.6 7.8 4.6

35.0 24.0 6.9 4.2 7.0 4.2 7.0 4.2 7.3 4.4 7.4 4.5 7.7 4.5 7.7 4.4

37.5 26.0 6.8 4.0 6.9 4.2 7.1 4.3 7.4 4.5 7.4 4.5 7.6 4.4 7.6 4.4

40.0 28.0 6.8 4.0 6.9 4.1 7.2 4.3 7.3 4.4 7.3 4.4 7.6 4.4 7.6 4.4

43.0 30.0 6.8 4.0 6.9 4.1 7.2 4.2 7.2 4.2 7.3 4.2 7.5 4.3 7.5 4.3

WB CA SHC CA SHC CA SHC CA SHC CA SHC CA SHC CA SHC

12.1.4 Heating Capacity (In combination with PUHY, PURY)

GUF-50RD3

SHC20SHC21SHC25SHC27SHC

-14.6 -15.0

DB WB

2.8 2.8 2.8 2.8 2.8

-11.5 -12.0 3.0 3.0 3.0 3.0 3.0

-9.5 -10.0 3.2 3.2 3.2 3.1 3.1

-6.9 -7.5 3.4 3.4 3.4 3.3 3.3

-4.3 -5.0 3.6 3.6 3.6 3.5 3.5

-1.8 -2.5 3.8 3.8 3.8 3.7 3.7

1.0 0 4.0 4.0 4.0 3.9 3.9

3.5 2.5 4.2 4.2 4.2 4.1 4.0

6.0 5.0 4.2 4.2 4.2 4.2 4.0

7.0 6.0 4.2 4.2 4.2 4.0 4.0

8.8 7.5 4.4 4.4 4.4 4.0 4.0

11.5 10.0 4.7 4.2 4.2 4.0 4.0

14.0 12.5 5.0 4.2 4.2 4.0 3.3

16.5 15.0 5.0 4.2 4.2 3.3 3.3

17.0 15.5 5.0 4.2 4.2 3.3 3.3

GUF-100RD3

SHC20SHC21SHC25SHC27SHC

-14.6 -15.0 5.6 5.6

-11.5 -12.0 6.0 6.0

-9.5 -10.0 6.3 6.3

-6.9 -7.5 6.7 6.7

-4.3 -5.0 7.1 7.1

-1.8 -2.5 7.5 7.5

1.0 0 7.9 7.9

3.5 2.5 8.3 8.3

6.0 5.0 8.3 8.3

7.0 6.0 8.3 8.3

8.8 7.5 8.7 8.7

11.5 10.0 9.3 8.3

14.0 12.5 9.9 8.3

16.5 15.0 10.0 8.3

17.0 15.5 10.0 8.3

5.6

6.0

6.3

6.7

7.1

7.5

7.9

8.3

8.7

8.3

5.6

6.0

6.3

6.7

7.1

7.5

7.8

8.2

8.3

8.0

6.5

5.6

5.9

6.3

6.7

7.1

7.5

7.8

8.0

6.5

*The above data shows an assumed value obtained by calculation.

DB WB

Outdoor inlet air temp (°C)

Correction factor

PUHY-P200/P250YGM-A PURY-P200/P250YGM-A

PUHY-P300YGM-A PURY-P300YGM-A

PUHY-P350YGM-A PURY-P350YGM-A

PUHY-P400YGM-A PURY-P400YGM-A

PUHY-P450/P500YGM-A PURY-P450/P500YGM-A

64210-2-4-6-8-10

1.0 0.95 0.84 0.83 0.83 0.87 0.90 0.95 0.95 0.95

1.0 0.93 0.82 0.80 0.82 0.86 0.90 0.90 0.95 0.95

1.0 0.93 0.85 0.83 0.84 0.86 0.90 0.90 0.95 0.95

1.0 0.95 0.90 0.87 0.88 0.89 0.90 0.95 0.95 0.95

1.0 0.98 0.89 0.86 0.89 0.90 0.92 0.95 0.95 0.95

12.2 Correction at frosting and defrosting

When a decrease in heating capacity due to frosted and defrosting operations is considered, the value multiplied by the correction factor in the table below represents the heating capacity. Refer to the City Multi Data Book for details.

12.2.1

R410A refrigerant unit

Correction factor table

12.3 Correction by temperature

12.3.1

R410A refrigerant unit

(1) Cooling

Standard specifications

●

Calculation

Capacity’ = Capacity × Ratio Input’ = Input × Ratio

Current’ =

Input’ × 1,000

3 × Source × 0.91

* Capacity’

Input’ After correction Current’

√

}

PUHY-

P200YGM-A

PUHY-

P250YGM-A

PUHY-

P300YGM-A

PUHY-

P350YGM-A

PUHY-

P400YGM-A

PUHY-

P450YGM-A

PUHY-

P500YGM-A

Capacity

6.14

380/400/415

10.3/9.8/9.4

22.4

7.72

13.0/12.3/11.9

28.0

9.57

16.1/15.3/14.7

33.5

11.39

19.2/18.2/17.6

40.0

13.42

22.6/21.5/20.7

45.0

13.61

22.9/21.8/21.0

50.0

15.59

26.3/25.0/24.0

56.0

Input

Source

Current

CHAPTER 1 ● Product Section

12.2.2 R22

refrigerant unit

Corection factor table

Outdoor inlet air temp (°C)

Correction factor

PUHY-200/250YEM-A PUHY-200/250YEMC-A PURY-200/250YEMC-A

PUHY-315YEM-A PUHY-315YEMC-A

PUHY-400/500YEM-A PUHY-400/500YEMC-A

6420-2-4 -6 -8 -10

1.0 0.95 0.84 0.83 0.87 0.90 0.95 0.95 0.95

1.0 0.93 0.82 0.82 0.86 0.90 0.90 0.95 0.95

1.0 0.98 0.89 0.89 0.86 0.90 0.92 0.95 0.95

CHAPTER 1 ● Product Section

The ratio of cooling power input

PUHY-P200/P250YGM-A

The ratio of cooling capacity

The ratio of cooling power input

PUHY-P300/P350/P400YGM-A

The ratio of cooling capacity

0.8

0.7

0.9

1.0

1.1

1.2

1.3

-5 0 5 10 15 20 25 30 35 40 45

Ratio

Indoor Temperature (˚CWB)

Outdoor Temperature (˚CDB)

24˚CWB

16˚CWB

18˚CWB

20˚CWB

22˚CWB

15˚CWB

0.8

0.7

0.9

1.0

1.1

1.2

1.3

-5 0 5 10 15 20 25 30 35 40 45

Ratio

Indoor Temperature (˚CWB)

Outdoor Temperature (˚CDB)

24˚CWB

16˚CWB

18˚CWB

20˚CWB

22˚CWB

15˚CWB

Ratio

Outdoor Temperature (˚CDB)

Indoor Temperature (˚CWB)

0.8

0.7

0.9

1.0

1.1

1.2

1.4

1.3

-5 0 5 10 15 20 25 30 35 40 45

24˚CWB

16˚CWB

18˚CWB

20˚CWB

22˚CWB

15˚CWB

0.8

0.7

0.6

0.9

1.0

1.1

1.2

Ratio

Indoor Temperature (˚CWB)

Outdoor Temperature (˚CDB)

24˚CWB

16˚CWB

18˚CWB

20˚CWB

22˚CWB

15˚CWB

-5 0 5 10 15 20 25 30 35 40 45

CHAPTER 1 ● Product Section

(2) Heating

Standard specifications

●

Calculation

Capacity’ = Capacity × Ratio Input’ = Input × Ratio

Current’ =

Input’ × 1,000

3 × Source × 0.91

* Capacity’

Input’ After correction Current’

√

}

PUHY-

P200YGM-A

PUHY-

P250YGM-A

PUHY-

P300YGM-A

PUHY-

P350YGM-A

PUHY-

P400YGM-A

PUHY-

P450YGM-A

PUHY-

P500YGM-A

Capacity

5.98

380/400/415

10.0/9.5/9.2

25.0

7.62

12.8/12.2/11.7

31.5

9.10

15.3/14.5/14.0

37.5

11.02

18.6/17.6/17.0

45.0

12.43

20.9/19.9/19.2

50.0

13.86

23.3/22.2/21.4

56.0

15.89

26.8/25.4/24.5

63.0

Input

Source

Current

The ratio of cooling power input

PUHY-P450/P500YGM-A

The ratio of cooling capacity

0.8

0.7

0.9

1.0

1.1

1.2

1.3

1.4

Ratio

Indoor Temperature (˚CWB)

Outdoor Temperature (˚CDB)

24˚CWB

16˚CWB

18˚CWB

20˚CWB

22˚CWB

15˚CWB

-5 0 5 10 15 20 25 30 35 40 45

0.8

0.7

0.5

0.6

0.9

1.0

1.1

1.2

Ratio

Indoor Temperature (˚CWB)

Outdoor Temperature (˚CDB)

24˚CWB

16˚CWB

18˚CWB

20˚CWB

22˚CWB

15˚CWB

-5 501015202530354045

CHAPTER 1 ● Product Section

The ratio of heating power input

PUHY-P200/P250YGM-A

The ratio of heating capacity

The ratio of heating power input

PUHY-P300/P350/P400YGM-A

The ratio of heating capacity

0.6

0.7

0.5

0.8

0.9

1.0

1.1

1.2

1.3

-20 -15 -10 -5 0 5 10 15

Ratio

Outdoor Temperature (˚CWB)

15˚CDB

20˚CDB

25˚CDB

27˚CDB

Indoor Temperature (˚CDB)

0.6

0.7

0.5

0.8

0.9

1.0

1.1

-20 -15 -10 -5 0 5 10 15

Ratio

Outdoor Temperature (˚CWB)

15˚CDB

20˚CDB

25˚CDB

27˚CDB

Indoor Temperature (˚CDB)

0.8

0.9

0.7

1.0

1.1

1.2

1.3

0.6

0.5

-20 -15 -10 -5 0 5 10 15

Ratio

Outdoor Temperature (˚CWB)

15˚CDB

20˚CDB

25˚CDB

27˚CDB

Indoor Temperature (˚CDB)

0.8

0.9

0.7

1.0

1.1

0.6

0.5

0.4

-20 -15 -10 -5 0 5 10 15

Ratio

Outdoor Temperature (˚CWB)

15˚CDB

20˚CDB

25˚CDB

27˚CDB

Indoor Temperature (˚CDB)

CHAPTER 1 ● Product Section

●

Calculation

Capacity’ = Capacity × Ratio Input’ = Input × Ratio

Current’ =

Input’ × 1,000

3 × Source × 0.91

* Capacity’

Input’ After correction Current’

√

}

12.3.2 R22 refrigerant unit

(1) Cooling

Standard specifications

PUHY-

200YEMC-A

PUHY-

250YEMC-A

PUHY-

315YEMC-A

PUHY-

400YEMC-A

PUHY-

500YEMC-A

PURY-

200YEMC-A

PURY-

250YEMC-A

Capacity

7.13

380/400/415

12.0/11.4/11.0

24.6

8.37

14.1/13.4/12.9

28.0

12.05

19.9/18.9/18.2

35.5

15.87

26.7/25.4/24.5

45.0

18.98

32.0/30.4/29.3

56.0

9.65

16.2/15.4/14.9

24.6

10.56

17.8/16.9/16.3

28.0

Input

Source

Current

The ratio of heating power input

PUHY-P450/P500YGM-A

The ratio of heating capacity

0.8

0.9

0.7

1.0

1.1

1.2

1.3

0.6

0.5

-20 -15 -10 -5 0 5 10 15

Ratio

Outdoor Temperature (˚CWB)

15˚CDB

20˚CDB

25˚CDB

27˚CDB

Indoor Temperature (˚CDB)

0.8

0.9

0.7

1.0

1.1

0.6

0.5

-20 -15 -10 -5 0 5 10 15

Ratio

Outdoor Temperature (˚CWB)

15˚CDB

20˚CDB

25˚CDB

27˚CDB

Indoor Temperature (˚CDB)

CHAPTER 1 ● Product Section

The ratio of cooling power input

PUHY-200/250/315YEMC-A

The ratio of cooling capacity

The ratio of cooling power input

PUHY-400/500YEMC-A

The ratio of cooling capacity

Ratio

Outdoor Temperature (˚CDB)

0.80

0.90

1.00

1.10

1.20

1.30

-5 5 15 25 35 45 50010203040

Indoor Temperature (˚CWB)

16˚CWB

18˚CWB

19˚CWB

20˚CWB

22˚CWB

24˚CWB

15˚CWB

Outdoor Temperature (˚CDB)

Ratio

0.50

0.70

0.90

1.10

1.30

0.40

0.60

0.80

1.00

1.20

-5 0 5 10 15 20 25 30 35 45 5040

Indoor Temperature (˚CWB)

19˚CWB

20˚CWB

22˚CWB

24˚CWB

15˚CWB

16˚CWB

18˚CWB

Ratio

Outdoor Temperature (˚CDB)

0.80

0.90

1.00

1.10

1.20

1.30

-5 5 15 25 35

45 50010203040

Indoor Temperature (˚CWB)

16˚CWB

18˚CWB

20˚CWB

22˚CWB

24˚CWB

15˚CWB

0.50

0.70

0.90

1.10

1.30

0.40

0.60

0.80

1.00

1.20

-5 0 5 10 15 20 25 30 35 40 45 50

Outdoor Temperature (˚CDB)

Ratio

Indoor Temperature (˚CWB)

24˚CWB 22˚CWB 20˚CWB 18˚CWB 16˚CWB 15˚CWB

CHAPTER 1 ● Product Section

●

Calculation

Capacity’ = Capacity × Ratio Input’ = Input × Ratio

Current’ =

Input’ × 1,000

3 × Source × 0.91

* Capacity’

Input’ After correction Current’

√

}

(2) Heating

Standard specifications

PUHY-

200YEMC-A

PUHY-

250YEMC-A

PUHY-

315YEMC-A

PUHY-

400YEMC-A

PUHY-

500YEMC-A

PURY-

200YEMC-A

PURY-

250YEMC-A

Capacity

6.66

380/400/415

11.2/10.6/10.2

25.0

8.77

14.8/14.0/13.5

31.5

10.91

18.2/17.3/16.6

39.1

14.31

24.1/22.9/22.1

50.0

17.92

30.2/28.7/27.7

63.0

7.66

12.9/12.2/11.8

25.0

9.74

16.4/15.6/15.0

31.5

Input

Source

Current

The ratio of cooling power input

PURY-200/250YEMC-A

The ratio of cooling capacity

0.80

0.90

1.00

1.10

1.20

1.30

-5 5 15 25 35 45010203040

Ratio

Indoor Temperature (˚CWB)

Outdoor Temperature (˚CDB)

16˚CWB

18˚CWB

19˚CWB

20˚CWB

22˚CWB

24˚CWB

15˚CWB

0.50

0.70

0.90

1.10

1.30

0.40

0.60

0.80

1.00

1.20

-5 0 5 10 15 20 25 30 35 40 45 Outdoor Temperature (˚CDB)

Ratio

19˚CWB

20˚CWB

22˚CWB

24˚CWB

15˚CWB

16˚CWB

18˚CWB

Indoor Temperature (˚CWB)

CHAPTER 1 ● Product Section

The ratio of heating power input

PUHY-200/250/315YEMC-A

The ratio of heating capacity

The ratio of heating power input

PUHY-400/500YEMC-A

The ratio of heating capacity

0.60

0.70

0.80

0.90

1.00

1.10

1.20

1.30

-15 -10 -5 0 5 10 15 20

Ratio

Indoor Temperature (˚CDB)

15˚CDB

20˚CDB

25˚CDB

27˚CDB

Outdoor Temperature (˚CWB)

Ratio

0.50

0.60

0.70

0.80

0.90

1.00

1.10

-15 -10 -5 0 5 10 15 20

15˚CDB

20˚CDB

25˚CDB

27˚CDB

Indoor Temperature (˚CDB)

0.60

0.70

0.80

0.90

1.00

1.10

1.20

1.30

-15 -10 -5 0 5 10 15 20

Outdoor Temperature (˚CWB)

Ratio

Indoor Temperature (˚CDB)

15˚CDB

20˚CDB

25˚CDB

27˚CDB

0.50

0.60

0.70

0.80

0.90

1.00

1.10

-15 -10 -5 0 5 10 15 20

Ratio

Indoor Temperature (˚CDB)

15˚CDB

20˚CDB

25˚CDB

27˚CDB

Outdoor Temperature (˚CWB)

CHAPTER 1 ● Product Section

The ratio of heating power input

PURY-200/250YEMC-A

The ratio of heating capacity

0.60

0.70

0.80

0.90

1.00

1.10

1.20

1.30

-15 -10 -5 0 5 10 15 20

Ratio

Outdoor Temperature (˚CWB)

Indoor Temperature (˚CDB)

15˚CDB

20˚CDB

25˚CDB

27˚CDB

0.50

0.60

0.70

0.80

0.90

1.00

1.10

-15 -10 -5 0 5 10 15 20

Ratio

Outdoor Temperature (˚CWB)

Indoor Temperature (˚CDB)

15˚CDB

20˚CDB

25˚CDB

27˚CDB

CHAPTER 1 ● Product Section

12.4 Correction by Refrigerant Piping Length

12.4.1 R410A refrigerant unit

To obtain a decrease in cooling/heating capacity due to refrigerant piping extension, multiply by the capacity correction factor based on the refrigerant piping equivalent length in the table below.

0.65

0.7

0.75

0.8

0.85

0.9

0.95

0204060 80100 120 140 160

Pinping equivalent length (m)

Cooling capacity

correction factor

100

150 200 260

Total capacity of indoor unit

(1) Cooling capacity correction

0.65

0.7

0.75

0.8

0.85

0.9

0.95

0204060 80100 120 140 160

Pinping equivalent length (m)

Cooling capacity

correction factor

150

225 300 390

Total capacity of indoor unit

PUHY-P300YGM-A, PURY-P300YGM-A

PUHY-P200YGM-A, PURY-P200YGM-A

0.7

0.75

0.8

0.85

0.9

0.95

0204060 80100 120 140 160

Pinping equivalent length (m)

Cooling capacity

correction factor

125

188 250 325

Total capacity of indoor unit

0.7

0.75

0.8

0.85

0.9

0.95

0204060 80100 120 140 160

Pinping equivalent length (m)

Cooling capacity

correction factor

175

263 350 455

Total capacity of indoor unit

PUHY-P350YGM-A, PURY-P350YGM-A

PUHY-P250YGM-A, PURY-P250YGM-A

0.75

0.8

0.85

0.9

0.95

Cooling capacity

correction factor

020406080100 120 140 160

Pinping equivalent length (m)

200

300 400 520

Total capacity of indoor unit

0.7

0.75

0.8

0.85

0.9

0.95

0204060 80100 120 140 160

Pinping equivalent length (m)

Cooling capacity

correction factor

250

375 500

650

Total capacity of indoor unit

PUHY-P500YGM-A, PURY-P500YGM-A

PUHY-P400YGM-A, PURY-P400YGM-A

0.75

0.8

0.85

0.9

0.95

Cooling capacity

correction factor

0204060 80100 120 140 160

Pinping equivalent length (m)

225

338 450 585

Total capacity of indoor unit

PUHY-P450YGM-A, PURY-P450YGM-A

CHAPTER 1 ● Product Section

0.9

0.95

020406080100 120

Pinping equivalent length (m)

Heating capacity

correction factor

(2) Heating capacity correction

0.8

0.82

0.84

0.86

0.88

0.9

0.92

0.94

0.96

0.98

020406080100 120 140 160

Pinping equivalent length (m)

Heating capacity

correction factor

PURY-P200YGM-A, PURY-P250YGM-A PURY-P300YGM-A

PUHY-P200YGM-A, PUHY-P250YGM-A

0.9

0.95

020406080100 120

Pinping equivalent length (m)

Heating capacity

correction factor

0.8

0.82

0.84

0.86

0.88

0.9

0.92

0.94

0.96

0.98

020406080100 120 140 160

Pinping equivalent length (m)

Heating capacity

correction factor

PURY-P350YGM-A, PURY-P400YGM-A

PUHY-P300YGM-A, PUHY-P350YGM-A PUHY-P400YGM-A, PUHY-P450YGM-A PUHY-P500YGM-A

0.8

0.82

0.84

0.86

0.88

0.9

0.92

0.94

0.96

0.98

020406080100 120 140 160

Pinping equivalent length (m)

Heating capacity

correction factor

PURY-P450YGM-A, PURY-P500YGM-A

●

How to obtain piping equivalent length

1) PUHY-P200YGM-A, PURY-P200YGM-A

Equivalent length = (Actual piping length to the farthest indoor unit) + (0.35 × number of bent on the piping) m

2) PUHY-P250/P300YGM-A, PURY-P250/P300YGM-A

Equivalent length = (Actual piping length to the farthest indoor unit) + (0.42 × number of bent on the piping) m

3) PUHY-P350YGM-A, PURY-P350YGM-A

Equivalent length = (Actual piping length to the farthest indoor unit) + (0.47 × number of bent on the piping) m

4) PUHY-P400/P450/P500YGM-A, PURY-P400/P450/P500YGM-A

Equivalent length = (Actual piping length to the farthest indoor unit) + (0.50 × number of bent on the piping) m

CHAPTER 1 ● Product Section

12.4.2 R22

refrigerant unit

Total capacity of indoor unit

Cooling capacity

correction factor

1.0

0.9

0.8

0.7 200406080 100 120

Piping equivalent length (m)

100

150

200

260

(1) Cooling capacity correction

Cooling capacity

correction factor

1.0

0.9

0.8

200406080 100 120

Piping equivalent length (m)

158 237

315

410

Total capacity of indoor unit

PUHY-315YEM-A/315YEMC-A

PUHY-200YEM-A/200YEMC-A

Total capacity of indoor unit

Cooling capacity

correction factor

1.0

0.9

0.8

0.7 200406080 100 120

Piping equivalent length (m)

125

188

250

325

200

300

400

520

Total capacity of indoor unit

Cooling capacity

correction factor

1.0

0.9

0.8

0.7

200406080 100 120

Piping equivalent length (m)

PUHY-400YEM-A/400YEMC-A

PUHY-250YEM-A/250YEMC-A

250

375

500

650

Total capacity of indoor unit

Cooling capacity

correction factor

1.0

0.9

0.8

0.7

20 40

80 100 120

Piping equivalent length (m)

Total capacity of indoor unit

Cooling capacity

correction factor

1.0

0.9

0.8

0.7 200406080 100 120

Piping equivalent length (m)

125

188

250

375

PURY-250YEMC-A

PUHY-500YEM-A/500YEMC-A

Total capacity of indoor unit

Cooling capacity

correction factor

1.0

0.9

0.8

0.7 200406080 100 120

Piping equivalent length (m)

100

150

200

300

PURY-200YEMC-A

CHAPTER 1 ● Product Section

Heating capacity

correction factor

1.0

0.9

0.8

0.7 200406080 100 120

Piping equivalent length (m)

(2) Heating capacity correction

Heating capacity

correction factor

1.0

0.9

0.8

0.7 200406080 100 120

Piping equivalent length (m)

PUHY-200YEM-A/200YEMC-A PUHY-250YEM-A/250YEMC-A

Heating capacity

correction factor

1.0

0.9

0.8

0.7 200406080 100 120

Piping equivalent length (m)

Piping equivqlent length (m)

Heating capacity

correction factor

1.0

0.9

20 40

80 100 120

PUHY-315YEM-A/315YEMC-A

Total capacity of indoor unit

Heating capacity

correction factor

1.0

0.9

0.8

0.7 200406080 100 120

Piping equivalent length (m)

100

150

200 or more

PURY-200YEMC-A

Total capacity of indoor unit

Heating capacity

correction factor

1.0

0.9

0.8

0.7 200406080 100 120

Piping equivalent length (m)

125

188

250 or more

PURY-250YEMC-A

PUHY-400YEM-A/400YEMC-A PUHY-500YEM-A/500YEMC-A

●

How to obtain piping equivalent length

1) PUHY-200YEM-A/200YEMC-A

Equivalent length = (Actual piping length to the farthest indoor unit) + (0.47 × number of bent on the piping) m

2) PUHY-250YEM-A/250YEMC-A

Equivalent length = (Actual piping length to the farthest indoor unit) + (0.50 × number of bent on the piping) m

3) PUHY-315YEM-A/315YEMC-A/400YEM-A/400YEMC-A

Equivalent length = (Actual piping length to the farthest indoor unit) + (0.70 × number of bent on the piping) m

4) PUHY-500YEM-A/500YEMC-A

Equivalent length = (Actual piping length to the farthest indoor unit) + (0.80 × number of bent on the piping) m

CHAPTER 1 ● Product Section

100

0 200 400 600

100

0 200 400 600 800 1000 1200

PZ-50RFM 466 174 2 GUF-50RDH3/50RD3

PZ-100RFM 561 236 2 GUF-100RDH3/100RD3

Dimension (mm)

Tested

dust

Measurement method

Filter type

Applicable

model

GUF-50RDH3 GUF-100RDH3 GUF-50RD3 GUF-100RD3

Protection of heat exchange element

Assurance of sanitary

environment

AFI

Gravitational

method

Compound

dust

ASHRAE

Colorimetric

method

Atomspheric

dust

Countingh method

(DOP method)

Application

JIS 14 types

DOP 0.8 µm

DOP 0.3 µm

82% 8% - 12% 5% - 9% 2% - 5%

99% 65% 60% 25%

Pre-filter NP/400 (EU3)

High Model PZ-50RFM efficiency PZ-100RFM filter

(EU7)(Optional parts)

Note: This is one set per main body.

PZ-50RFM PZ-100RFM

External static pressure (Pa)

Air volume (m3/h) Air volume (m3/h)

13. Filter Characteristics

13.1 Filter Types

13.2 High-Efficiency Filter (Optional Parts)

13.3 Pressure Loss

Pressure loss characteristics

AIR

FLOW

Model

Number of

filters per set

Applicable model *

CHAPTER 1 ● Product Section

The ability of the filters used within the OA processing units are shown below, expressed in terms of collection ratio (%).

100

Collection ratio (%)

High efficiency filter

NP/400

0.2 0.3 0.4 0.6 0.8 1.0 2.0 3.0 4.0 6.0 8.0 10.0

20 30

40 60 80 100

Particle diameter (µm)

Dust removal retention characteristics (NP/400 + High efficiency filter)

GUF-50RDH3/50RD3

0 100 200 300 350

400

50 150 250

100

140

120

Presure loss (Pa)

Dust removal volume (g/set)

GUF-100RDH3/100RD3

100 200 300 400 500 600 700

100

180

200

160

140

120

Presure loss (Pa)

Dust removal volume (g/set)

CHAPTER 1 ● Product Section

14. Noise Characteristics

14.1 GUF-50RDH3/50RD3

14.2 GUF-100RDH3/100RD3

●

Measurement Condition

NC-70

NC-60

NC-50

NC-40

NC-30

NC-20

NC-10

Directly below (Measurement point A)

Octave band sound level (dB)

Octave band central frequency (Hz)

Supply/

Exhaust air

Main unit

To indoor unit

NC-70

NC-60

NC-50

NC-40

NC-30

NC-20

NC-10

Outlet (Measurement point B)

Octave band sound level (dB)

Octave band central frequency (Hz)

NC-70

NC-60

NC-50

NC-40

NC-30

NC-20

NC-10

Directly below (Measurement point A)

Octave band sound level (dB)

Overall

Octave band central frequency (Hz)

62.5 125 250 500 1K 2K 4K 8K Overall 62.5 125 250 500 1K 2K 4K 8K

Overall 62.5 125 250 500 1K 2K 4K 8K Overall 62.5 125 250 500 1K 2K 4K 8K

NC-70

NC-60

NC-50

NC-40

NC-30

NC-20

NC-10

Outlet (Measurement point B)

Octave band sound level (dB)

Octave band central frequency (Hz)

Measurement site:

Mitsubishi Electric Co.,

Nakatsugawa Works

Anechoic chamber

1.5 m

High Low

CHAPTER 1 ● Product Section

Test report

This document reports the result that there is no bacterial cross contamination for the Lossnay Core.

(1) Object

The object of this test is to verify that there is no bacterial cross contamination from the outlet air to the inlet air of the Lossnay Core in the heat exchange process.

(2) Client

MITSUBISHI ELECTRIC CO. NAKATSUGAWA WORKS.

(3) Test period

April 26, 1999 - May 28, 1999

(4) Test method

The configuration of the test equipment is shown below. The test bacteria suspension is sprayed in the outlet duct at a pressure of 1.5 kg/cm2with a sprayer whose dominant particle size is 0.3 - 0.5 µm. The air sampling tubes are installed at the each center of the locations of A, B, C, D, in the Lossnay Core inlet/outlet ducts so that their openings are directly against the air flow, and then connected to the impinger outside the duct. The impinger is filled with 100 mL physiological salt solution. The airborne bacteria in the duct air are sampled at the rate of 10L air/minute for three minutes.

(5) Test bacteria

The bacteria used in this test are as followed;

Bacillus subtilis IFO 3134 Pseudomonas diminuta IFO14213 (JIS K 3835 Method of testing bacteria trapping capability of precision filtration film elements and modules; applicable to precision filtration film, etc. applied to air or liquid)

(6) Test result

The result of the test with Bacillus subtilis is shown in Table 1. The result of the test with Pseudomonas diminuita is shown in Table 2.

Sprayer

Impinger

Fan

Safety cabinet

Impinger

LOSSNAY Core

HEPA filter

15. Reference Documents

15.1 The Result of No Bacterial Cross Contamination for the Lossnay Core and Determining Resistance of the Lossnay Core to Molds

CHAPTER 1 ● Product Section

Table 1 Test result with bacillus subtilis (CFU/30L air)

No. ABCD

1 5.4 × 10

5.6 × 10

<10

2 8.5 × 10

7.5 × 10

<10

3 7.5 × 10

<10

4 1.2 × 10

1.2 × 10

<10

5 1.8 × 10

1.5 × 10

<10

Average 2.0 × 10

1.5 × 10

<10

Table 2 Test result with pseudomonas diminuita (CFU/30L air)

No. ABCD

1 3.6 × 10

2.9 × 10

<10

2 2.5 × 10

1.2 × 10

<10

3 2.4 × 10

7.2 × 10

<10

4 3.4 × 10

8.4 × 10

<10

5 1.7 × 10

3.8 × 10

<10

Average 2.7 × 10

4.7 × 10

<10

(7) Considerations

Bacillus subtilis is commonly detected in the air and resistant to dry. Pseudomonas diminuita is susceptible to dry and only a few exists in the air. However, it is used in the performance verification of the bacteria trapping filter since the particle size is small (Cell diameter; 0.5 µm: Cell length 1.0 to 4.0 µm). Both Bacillus subtilis and Pseudomonas diminuta are detected at the location A and B in the outlet side duct where they are sprayed, but neither them are detected at location C (in the air filtered by the HEPA filter) and the location D (in the air crossed in the Lossnay Core) on the inlet side. Since the number of bacteria in the location A is substantially equal to one in the location B, it is estimated that only a few bacteria are attached to the Lossnay Core on the outlet side. Also, no test bacteria is detected at the location D where the air is crossed in the Lossnay Core. Therefore, it can be concluded that the bacteria attached to the outlet side will not pass through the inlet side even after the heat is exchanged.

Shunji Okada Manager, Biological Section Kitasato Reseaarch Center of Enviromental Seiences

CHAPTER 1 ● Product Section

Test report

This document reports the result of determining resistance of the Lossnay Core to molds.

(1) Object

The object of this test is to determining resistance of the Lossnay Core to molds.

(2) Client

Mitsubishi Electric Co. Nakatugawa Works

(3) Test sample

Lossnay Core (paper separator)

(4) Test period

April 26, 1999 - May 28, 1999

(5) Test method

The testing method is in accordance with “5. General Industrial Products,” “Test Method of Resistance to Mold,” JIS Z 2911. The Lossnay Core is cut into 5 × 5 cm square. pole. The test mold spore solution is sprayed on one side of the core and, after covering one side of the crossing core with sponge sheet, the core is left in the chamber with 27°C, (relative humidity 95%) for four weeks.

(6) Test mold

The molds used in this test are as follows;

Aspergillus niger ATCC 6275 Penicillium citrinum ATCC 9849 Rhizopus oryzae IFO 31005 Cladosporium cladosporioides IFO 6348 Chaetomium globosum ATCC 6205

(7) Determination criterion

Observed growth on specimens Degree

None growth 3

Light growth (less than 1/3 area) 2

Heavy growth (more than 1/3 area) 1

(8) Test result

No hypha was grown in the place where the test mold spore solution was applied. So the degree of resistance to mold was judged to be 3.

Shunji Okada Manager, Biological Section Kitasato reseaarch Center of Enviromental Seiences

CHAPTER 1 ● Product Section

Material, Mixture ratio, Organization, Fan number, Density, Weight (g/m

)

15.2 Flame-proofing Properties of Lossnay Core

The Lossnay Core satisfied all requirements of Paragraph 4-3 of the Fire Prevention Law Enforcement Rules. Details of the tests carried out are as seen below.

Notation format 2 - (3)

Notification of flame-proofing property test

(For flame-proof materials and related items)

Flame-proofing committee test No., B-80028 April 17, 1980

Messrs.: Mitsubishi Electrical Corporation

Japan Flame-proofing committee

The results of the test, requested on April 8, 1980, are as follows.

Whereas

Part name

Product name (Brand)

Air filter Total heat exchanger

Lossnay (ventilation fan) B

Specially treated paper:

(Partition (white): Thickness 0.2 mm) (Filler block (blue): Thickness 0.2 mm)

Adhesive agent:

Vinyl acetate (Specific gravity ratio 2.6 %) 600 g/m

Residual Residual

Carbonized

Test No. Test item flame dust area

(sec.) (sec.) (cm2)

2-min.

1 (Vertical) 0. 4.1 35.4

heating

2 (Vertical) 0. 7.7 38.2

6-sec.

(Horizontal)

0. 1.4 35.9

heating after

1 (Vertical) 0. 0. 26.3

igniting

(Horizontal)

0. 0. 20.3

Test item

Carbonization No. of flame

length

contact times

Test No.

(cm) (times)

Evaluation Passing

Remarks

Test method

Application of Paragraph 4-3 Standards of Fire Prevention Laws Enforcement Rules (Ministry of Home Affairs Ordinance No. 6, 1961) (Thick cloth test)

Passing standards

Residual flame : 5 sec. or less Residual dust : 20 sec. or less Carburized area : 40 cm

or less

Washing test

CHAPTER 1 ● Product Section

Applicant

Company name Mitsubishi Electric Corp., Nakatsugawa Works

Address 1-3 Komanba-cho, Nakatsugawa, Gifu

Specimen type

Single-face laminated

Product

Lossnay Core

corrugated board

name

(Total heat recovery unit)

Single-face laminated corrugated board

... Thickness: 4 mm (Single-face corrugated board with 2 mm cell size laminated alternately at right angle) Partition (Liner paper) Flame-proof treated paper

...

Thickness: 0.085 mm, Weight: 70 g/m

Material structure and Adhesive agent ... Vinyl acetate resin

Specimen cross-sectional ...

Weight: 30 g/m2(Solid)

and test body diagram, etc. Filler (Flute paper)

... Colored wood free paper

...

Thickness: 0.093 mm, Weight: 79 g/m

Adhesive agent

... Vinyl acetate resin

... Weight: 30 g/m

(Solid) Partition (Liner paper) Flame-proof treated paper

...

Thickness: 0.085 mm, Weight: 70 g/m

Test body size and

300 (Long side) × 200 (Short side) × 4 (Thickness)

thickness (mm)

Test body direction The longer side is the vertical side.

Testing standards

Pre-treatment of Heating

Heating surface class and direction

Testing

test body time

method

JIS A 1322

Method A

The direction of which the corrugated

(45° Meckelian burner

(drying method)

3 min. board fold was vertical was set as the

method) front of the heating surface.

Test date October 5, 1993

Test position

Residual

Carbonized Discoloration

frame dust

length (Vertical ×length (Vertical

Remarks

Test results Class Direction No.

(sec.) (sec.)

Horizontal) (cm) Horizontal) (cm)

10 08.2 × 4.7 18.7 × 7.3

Front Vertical 2 0 0 8.4 × 4.9 24.3 × 7.8 *1

30 07.4 × 5.0 22.0 × 8.4

Evaluation

The specimen conforms to Class 2 flame-proofing (heating time: 3 min.) according to the “Fire retardancy test methods of thin materials for construction” as set forth by JIS A 1322.

Material Testing Laboratory

Persons in charge of testing Laboratory chief: Hiroshi Tamura, Technicians: Shigeru

Fujikawa, Nobuaki Oohiro, Tetsuya Ogawa

The Lossnay Core was also tested at the Japan Construction General Laboratories according to the fire retardancy test methods of thin materials for construction as set forth by JIS A 1322. The material was evaluated as Class 2 flame retardant. Details of the tests carried out are shown below.

Flame-proofing property test report

Messrs. Mitsubishi Electric Corp.,

Nakatsugawa Works

Acceptance No. VF-93-11-(2)

Data of acceptance September 7, 1993

Data of report October 12, 1993

Japan Construction General Laboratories

5-8-1 Fujishirodai, Suita City 565

Tel: 06-872-0391

Hiorshi Wakabayashi Dr. of Engineering, Director

Note: Immediately after starting heating, the flame was ignited simultaneously with the generation of smoke.

Penetration was observed approx. 2 min. 30 sec., after heating was started. There were no further changes.

4mm

2mm

CHAPTER 1 ● Product Section

Testing facility General Building Research Corporation

Address 1-3 Komanba-cho, Nakatsugawa, Gifu Company

Mitsubishi Electric Corporation

name

Nakatsugawa Works

Testing

According to “soundproofing effect test” in

method

Ministry of Construction No. 108

Measurement

March 9, 1979

date

Measurement

Temperature: 12.5°C, humidity: 77%

conditions

Soundproof area

W 580 × H 190

dimensions

Centre frequency

125 Hz 500 Hz 2,000 Hz 1 101.5 96.5 98.5 2 99.0 — — 3 100.0 97.5 98.5 4 102.0 — — 5 101.5 96.5 98.5

Average

100.9 96.9 98.5

level

1 81.5 63.5 53.0 2 79.5 — — 3 79.5 63.0 43.0 4 82.5 — — 5 81.5 62.5 43.5

Average

81.1 63.0 43.2

level Average sound pressure level

19.8 33.9 55.3

difference (dB) Sound absorbed by reverberation chamber on

2.79 3.90 7.22

reception side (m

)

Sound transmis-

5.8 18.4 37.1

sion loss (dB)

Refer to page 39 for details of test results

Remarks

The soundproofed area of the specimen is small in this test, and as the transmission of sound though the surrounding concrete block wall cannot be ignored, the concrete block wall was measured after the main test, and the main test measurement results were corrected.

Persons in charge of testing: Mitsuo Morimoto, Toshifumi Murakami

Measurement results

Each measured sound pressure level (dB)

Certificate

IVA-78-122

number

Product name

LGH-50E

Item name Heat exchange-type ventilator Application Ventilation Date of

October 1978

manufacture Place of

General Building Research Corporation

assembly Dimensions W 1250 × H 310 × D 1589 Area

———

concentration Remarks An existing hole (4000 mm × 3000 mm) was

covered with a hollow concrete block with Cultures, double-faced mortar (thickness 20 mm each), specimen with a wood frame with inner dimension of installation 580 mm × 190 mm × 230 mm being installed. method at The supply/exhaust box and duct was test facility mounted in this, and the main unit and

weather cover was mounted.

Peripheral

Oil clay was filled around the sound source

sections

Specimen configuration (dimensions mm) Refer to appendix 1, 2 for details. S: 1/20

15.3 Lossnay Core’s Soundproofing Properties Test

As the Lossnay Core is made of paper and the permeable holes are extremely small, the Element has outstanding soundproofing properties and is appropriate for ventilation in soundproof rooms. For example, the exposed ceiling-type LGH-50E has soundproofing characteristics of 33.9 dB with a center frequency of 400 Hz. This means that a sound source of 96.9 dB can be shielded to 63 dB.

Soundproofing effect test results

For Mitsubishi Electric Corporation

Nakatsugawa Works

Test number IVA-78-122

Acceptance data : February 22, 1979

Report : May 24, 1979

General Building Reseach Corporation

Fujishirodai 5-125, Suita-shi, Osaka-Fu, Japan

Person in charge of testing: Takeshi Tokura

No. 122-1

The results of the tests are as noted below.

General Building Research Corporation

General Manager, S. Okushima

Remarks

Urethane foam (15 mm thick) was stuck onto the inside of the duct and feed/exhaust box.

Specimen

Client

Sound source side

Reception side

Measurement pointMeasurement point

Sound transmission loss test

Steel plate thickness: 0.8

Internal flange hole with fixing screw

Weather cover Steel plate thickness: 0.6

Wood frame thickness: 20

Flange steel plate thickness: 1.6

Duct steel plate thickness: 1.6

Urethane foam thickness: 15 0.072 m

Feed/exhaust box Steel plate thickness: 1.0

Sound

reception side

Sound

source side

Mortar

CHAPTER 1 ● Product Section

15.4 Result of Microbial Test of Permeable Film Element

Microbial Test Report of Permeable Film Element

Kitasato Research Center of Environmental Science: Report No. 7858

March 3

1998

Kitasato Reseach Center of Environmental Science

The chairman: Ichiro Yamamoto

CHAPTER 1 ● Product Section

Microbial Test Report of Permeable Film Element

(1) Purpose of test

This test was conducted for the purpose of confirming whether or not microorganisms (Legionella) present in humidified water are released into humidified air after passing through an original permeable film humidifier element manufactured by Mitsubishi Electric Corporation.

(2) Party requesting test

Lossnay Manufacturing Department, Nakatsugawa Works, Mitsubishi Electric Corporation. Address: 1-3 Komanba-cho, Nakatsugawa City, Gifu Prefecture

(3) Test apparatus

Blower: Straight centrifugal fan, Model BFS-40S Humidifier-mounted ducts: Air sampling pipes (copper pipes) are attached to sites located approximately 20 cm in front of and behind the humidifier. The opening of the air intake pipe is positioned in the center of the ducts facing the flow of air, and connected to a sampler outside the ducts while gently bending along an L-shaped curve. Apparatus operation: Dry air blown in with the sirocco fan passes through the humidifier element and circulates to the air inflow port of the sirocco fan with a bellows duct having a diameter of 200 mm. Air samplers: Impingers are filled in advance with 100 ml aliquots of sterile physiological salt solution, after which one is connected upstream from the humidifier while another is connected downstream from the humidifier. Sampled air is then sprayed into the physiological saline to clean. The amount of air sampled into the impingers is set at 10 liters per minute. An under-sensor sampler consists of media placed on each level below the six levels of porous nozzles gradually decreasing in size, and blows air collected at the rate of 28.3 liters per minute onto the surface of agar media.

(4) Test organism

Legionella pneumophilla ATCC 33154

(5) Test method

1) Detection of test organism in humidified air

A suspension of test organisms at 1.4 × 10

CFU/ml is injected into the humidifier tank, after which the suspension is allowed to fill the element by natural inflow. The blower is operated after which air is collected into the sampler placed in the humidifier ten minutes later. The amount of sampled air and the air conditions at that time are shown in Table 1. Measurement of microbial count using the impinger method is performed by using physiological salt solution immediately after air sampling as the undiluted liquid, preparing a 10-fold serial dilution, inoculating 0.1 ml of that diluted liquid onto the surface of pour media B-CYEa agar media (Eiken Chemical) and incubating at 37°C for 4 days followed by counting the number of colonies formed. Only those colonies that form on B-CYEa agar media after re-inoculating onto B-CYEa agar media and blood agar media are counted as Legionella. With respect to the under-sensor sampler method, colonies that are formed using pour media WYOa agar media (Eiken Chemical) are re-inoculated onto B-CYEa agar media and blood agar media, and those colonies that formed only on the B-CYEa agar media are counted as Legionella.

CHAPTER 1 ● Product Section

Table 1 Air sampling conditions

Impinger method Slit sample method

Measurement

Sampled air volume

Humidity of circulated air

Sampled air volume

Humidity of circulated air

1st 20 lit. 26.5% 28.3 lit. 35.6%

2nd 40 lit. 29.4% 141.5 lit.

****

3rd 100 lit. 52.8% 141.5 lit.

****

4th 100 lit.

****

141.5 lit.

****

5th 100 lit. 36.1% 141.5 lit. 93.4%

2) Detection of test organisms on the surface of the permeable film

20 ml of a suspension of test organisms (5.8 × 10

CFU/ml) are injected into one bag of the permeable film humidifier element after which organisms are sampled and detected from the surface of the element bag one hour later. The sampling methods consist of: (1) sampling water droplets that formed on the surface of the front side of the element (side where the spacer frame is not attached) with a sterile syringe, (2) stamping the front surface and back surface (surface where the spacer frame is attached) of the element onto the surface of a medium, and (3) wiping both surfaces of the element (measuring 5 × 5 cm2each) with sterile solid gauze (Booth: Sawada Menko) and inoculating directly onto the surface of a medium.

Using pour media WYOa agar media (Eiken Chemical) for the medium, the formed colonies are reinoculated onto B-CYEa agar media and blood agar media followed by only counting those colonies that formed on B-CYEa agar media as Legionella.

(6) Test period

January 12, 1998 - January 28, 1998

(7) Test results

1) Detection of airborne test organisms in humidified air

The detection status of test organisms in the impinger method and slit sampler method is shown in Table 2. Although two types of sampling methods were used, test organisms were unable to be detected in circulating air in either of the methods.

Table 2 Detection of airborne test organisms in humidified air

Measurement

Impinger method Slit sampler method

(CFU/Sampled air volume) (CFU/Sampled air volume)

1st <10

CFU / 20 lit.> <102CFU / 28.3 lit.>

2nd <10

CFU / 40 lit.> <102CFU / 141.5 lit.>

3rd <10

CFU / 100 lit.> <102CFU / 141.5 lit.>

4th <10

CFU / 100 lit.> <102CFU / 141.5 lit.>

5th <10

CFU / 100 lit.> <102CFU / 141.5 lit.>

2) Detection of test organisms on the surface of the permeable film element

The detection status of test organisms from the surface of the permeable film humidifier element is shown in Table 3.

(A) Test organisms were unable to be detected from water droplets that formed on the surface of the

front side (side on which the spacer frame is not attached). Since water droplets did not form on the surface of the back side (surface in contact with the spacer frame), the test was unable to be performed.

(B) In the case of pressing the test surface of the element onto the surface of the medium, test

organisms were not detected for either surface.

CHAPTER 1 ● Product Section

detected on the surface of the front side (side in which the spacer frame is not attached). Seven colonies were detected from one of two locations on the surface of the back side (surface in contact with the spacer frame). Test organisms were unable to be detected at the other location.

Table 3

Surface for sampling test organisms from permeable film element

Sampled Method

Front surface (Where spacer frame is not attached)

Back surface (in contact with spacer frame)

Sampling site No.1 Sampling site No.2 Sampling site No.3 Sampling site No.4

Culturing of water droplets

Not detected Not detected No droplets No droplets

Stamping method Not detected Not detected Not detected Not detected

Wiping method Not detected Not detected Detected Not detected

(8) Discussion

The test organism of Legionella pneumophilla was unable to detected in humidified air of a humidifier using a permeable film humidifier element. Thus, a study was conducted by more directly injecting a suspension of the test organism inside the permeable film humidifier element to assess whether or not the test organisms permeate to the front side of the film element. As a result, although test organisms were unable to be detected in water droplet culturing and stamping methods, test organisms were detected from one sampling site on the back side in the wiping method. The number of detected test organisms were 7 CFU per unit area of 5 × 5 cm. Since about 5.8 × 102CFU ought to be detected even if the amount of liquid that seeped from the element is assumed to be 1 µl (organism suspension injected into the element: 5.8 × 105CFU/ml), it was assumed that only an extremely small amount of liquid actually seeped out. When considering that this seepage only occurred at one location of the 4 sites that were wiped, and that the amount of test organisms that seeped from the element is extremely small, it is believed that the organisms were detected as a result of damaging the film surface during wiping. Thus, it was concluded that Legionella pneumophilla does not seep through the permeable film humidifier element provided the surface of the element is not damaged by wiping or other form of abrasion.

Shunji Okuda, Test Director

CHAPTER 2

Air Conditioning System

Design Section

RARA SA

SA SA

RA SA

CHAPTER 2 ● Air Conditioning System Design Section

1. Guide to a Comfortable Air Conditioning System

Air conditioning is more than simply adjusting the temperature of the air. It is used for properly maintaining the conditions for the air in a given space including the temperature, CO and CO2 levels, the density of contaminant properties (removing odors created by humans and other things), air flow and its distribution. Recently, more attention has been placed on what an air conditioning system can do in addition to controlling temperature to improve the environment in a given space. This has given rise to demands for improved comfort, operating control for individual rooms, low-energy consumption, low maintenance and more compactness. Ceiling installation of units for cooling a floor or a particular zone, and functions such as the introduction of outdoor air, exhaust air removal, dust removal, heat recovery from ventilated air, heat processing and humidifying have been developed in response to these demands. In addition, by combining the OA processing unit with fin coil units or packaged air conditioners, comprehensive air conditioning can be provided.

1.1 Elements of Air Conditioning to be Considered

1.2 Example of a Comfortable Air Conditioning System

Adjusting the properties of the air

Control CO and CO2 densities and expelling airborne dust and odors

Reduce ventilation load

Maintain humidity levels. Important

especially

during winter

Especially remove tobacco smoke (Smoke that cannot be processed by ventilation)

Cooling or heating and maintaining desired temperature

Ventilation

Adjusts indoor static pressure (Inside and outside room)

1. Individual fans for intake and exhaust

2. Use individual static pressure adjustment units

1. High-efficiency filter

2. Total heat recovery unit (Lossnay Core)

Uses heat

exchanger

1. Direct Expansion coil

2. Use humidifier (permeable film type)

Uses high-efficiency filter

Refrigerant amount can be controlled in response to load

1. Remove contaminants from outdoor air

2. Trouble-free and easy to maintain

3. Process un-recovered heat load.

4. Assist in cooling or heating

1. Preheat for humidifying

2. Clean humidifying

3. Long service life free of mechanical trouble or becoming dirty

1. Remove tobacco smoke

2. Long service life

Maintain room temperature at ± 0.5°C (However, maintains air flow and volume at proper levels)

Heat recovery Humidifying Dust removal

Controlling room temperature

Heating or cooling

Outdoor air processing unit

Ventilation

Heat recovery

Cooling

and

heating

Humidifying

Dust removal

Fan (Exhaust)

Total heat recovery unit

Fan (Supply)

Direct Expansion coil

(Cooling, heating)

Humidifier (Adds humidity)

High-efficiency filter for supply air (Dust removal)

Filter for exhaust air (Dust removal)

Filter Filter

Direct Expansion coil Direct Expansion coil

Indoor unit

Cooling or heating

Dust removal

Air flow

]

][

[

CHAPTER 2 ● Air Conditioning System Design Section

2. Features of the OA Processing Unit

(1) Provides individual control for comprehensive air conditioning

By combining the OA processing units in each air conditioning zone with heating and cooling units, comprehensive air conditioning can be provided with control each individual zone. This individual air conditioning can include the operation and stopping of cooling and heating, ventilation, humidifying, heat processing, dust removal and heat recovery.

(2) Provides more design freedom and effective utilization of space

The OA processing unit is recessed into the ceiling so there is no need for a separate equipment room and elaborate duct work. In addition, if a ceiling mounted cooling and heating unit is selected, absolutely no floor space is required for the system. This eases design constraints and helps to eliminate problems related to the installation of the equipment room and noise and vibration from the main duct work.

(3) High static pressure outside the unit allows for extended duct length

Since a high static pressure outside the unit can be attained, extending ducts, adding branches or positioning of outlets can be done with relative freedom. This is a system that allows for a wide range of flexibility during installation.

(4) Long-life high-efficiency filter can be added

The high-efficiency filter offers up to 65% filtration (colorimetric method) and can be used for up to 3,000 hours without maintenance. There is space provided inside the OA processing unit for installing this optional filter.

(5) Low-energy consumption

This system does not need the large conveyance power required by previous systems. In addition, individual control and heat recovery by the internal Lossnay Core help to reduce energy consumption needs. In addition, the cooling and heating unit is compact in size.

(6) Can calculate electrical costs for each zone

When used in conjunction with packaged air conditioning, electricity consumption for each zone can be calculated, making this system perfect for use in buildings with tenants.

(7) Low noise

The noise level is low enough for the system to be used in virtually any application, including offices.

(8) Permeable film humidifier used

This is a clean type of humidifier that is compatible with the electronic components found in today’s “intelligent buildings”.

Examples of air conditioning systems

OA processing unit

(Ventilation, Heat recovery, Cooling and Heating, Humidifying, Dust removal)

Indoor unit

Note: Both the gas and liquid refrigerant lines are shown by a single line in the drawing.

City Multi

CHAPTER 2 ● Air Conditioning System Design Section

3. Air Conditioning and Ventilation

Fresh outdoor air must be introduced constantly at a set ratio in an air conditioning system. This fresh air is introduced to be mixed with the return air from the room, to adjust the temperature and humidity, supply oxygen, reduce body and other odors, remove tobacco smoke and to increase the cleanness of the air. The standard ventilation (outdoor air intake) volume is determined according to the type of application, estimated number of persons in the room, room area, and relevant regulations. Systems which accurately facilitate these requirements are increasingly being required to be installed in buildings.

3.1 Necessity of Ventilation

The purpose of ventilation is basically to supply oxygen, clean the air and control the temperature and humidity. Cleaning the air includes the elimination of odors, gases, dust and bacteria. Ventilation fills fundamental needs such as providing personal comfort and ensuring the necessary environment for the animals, plants and equipment in the area.

3.1.1 Effect of air contamination on human bodies

Effect of oxygen (O2) concentration

Concentration (%) Standards and effect of concentration changes

Approx. 21 Standard atmosphere.

20.5

Ventilation air volume standard will be a guideline where concentration does not decrease more than 0.5% from normal value. (From Japanese building code)

20 - 19

An oxygen deficiency of this amount does not directly endanger life in a normal air pressure, but if there is a combustion device in the area, the generation of CO will increase rapidly due to incomplete combustion.

18 Japanese Labor Safety and Sanitation Law standards. (Hypoxia prevention regulations.)

16 Normal concentration in exhaled air.

16 - 12 Increase in pulse and breathing resulting in dizziness and headaches.

15 Flame in combustion devices will extinguish.

12 Threat to life in short term.

7 Fatal

Concentration (ppm)

Effect of concentration changes

0.01 - 0.2 Standard atmosphere.

5 Considered to be the long-term tolerable value.

From Japanese building code, Building Management Law standards. Environmental standard 24-hour average.

Considered to be the short-term tolerable value. Environmental standard 8-hour average.

Tolerable concentration for labor environment. (Japan Industrial Sanitation Association)

100

No effect for 3 hours. Effect noticed after 6 hours. Headache, illness after 9 hours; harmful for long-term but not fatal.

200 Light headache in the forehead in 2 to 3 hours.

400 Headache in the forehead, nausea in 1 to 2 hours; headache in the back of head in 2.5 to 3 hours.

800 Headache, dizziness, nausea, convulsions in 45 minutes. Comatose in 2 hours.

1,600 Headache, dizziness in 20 minutes. Death in 2 hours.

3,200 Headache, dizziness in 5 to 10 minutes. Death in 30 minutes.

6,400 Death in 10 to 15 minutes.

12,800 Death in 1 to 3 minutes.

Several 10,000 ppm

(Several %)

This level may be found in automobile exhaust.

Effect of carbon dioxide (CO2)

Concentration (%) Effect of concentration changes

0.03 (0.04) Standard atmosphere.

0.04 - 0.06 City air.

0.07 Tolerable concentration when many people stay for long time.

0.10

General tolerable concentration. From Japanese building code, Building Management Law standards

0.15 Tolerable concentration used for ventilation calculations.

0.2 - 0.5 Considered as relatively poor.

0.5 or more Considered as the poorest.

0.5 Long-term safety limits (U.S. Labor Sanitation) ACGIH, regulation of laborer offices.

2 Depth of breathing and inhalation volume increases 30%.

3Work and physical functions deteriorate, breathing doubles.

4 Normal exhalation concentration.

4 - 5

The respiratory center is stimulated; depth and times of breathing increases. Dangerous if breathed in for a long period. If an O

2 deficiency also occurs, trouble will occur sooner and be more dangerous.

When breathed in for 10 minutes, breathing difficulties, redness in the face and headaches will occur. The trouble will worsen when there is also a deficiency of O

18 or more Fatal

Apprpx. 5 ppm is an annual average value in city areas. This value may exceed 100 ppm near roads, in tunnels and parking areas.

CHAPTER 2 ● Air Conditioning System Design Section

Effect of carbon monoxide (CO)

10,000 ppm = 1%

There is no toxic level in CO2 alone. However, these tolerable concentrations are a guideline of the contamination estimated when the physical and chemical properties of the air deteriorate in proportion to the increase of CO2.

Note: According to Facility Check List published by Kagekuni-sha.

3.1.2 Effect of air contamination in buildings

Dirtiness of interior

New ceilings, walls and ornaments will turn yellow in one to two years. This is caused by dust and the tar in tobacco smoke.

CHAPTER 2 ● Air Conditioning System Design Section

3.2 Ventilation Method

3.2.1 Ventilation class and selection points

An appropriate ventilation method must be selected according to the purpose. Ventilation is composed of “Supply air” and “Exhaust air” functions. These functions are classified according to natural flow or mechanical ventilation using a fan (forced ventilation).

Classification of mechanical ventilation

Classification of ventilation (according to Building Standards Law)

Supply Exhaust Ventilation volume Room pressure

Class 1 Mechanical Mechanical Random (constant) Random Class 2 Mechanical Natural Random (constant) Positive pressure Class 3 Natural Mechanical Random (constant) Negative pressure Class 4 Natural Mechanical & natural Limited (inconstant) Negative pressure

1. Class 1 ventilation

Fresh outdoor air is mechanically brought in and simultaneously the stale air in the room is mechanically discharged.

2. Class 2 ventilation

Fresh outdoor air is mechanically brought in and the exhaust air is discharged from the exhaust air outlet (natural).

3. Class 3 ventilation

The stale air in the room is mechanical-ly discharged and simultaneously fresh outdoor air is mechanically introduced from the supply air diffuser (natural).

Ex. of application

•Ventilation of air conditioned rooms. (buildings, hospitals, etc.)

•Ventilation of room not facing an outer wall. (basement, etc.)

•Ventilation of large room. (office, large conference room, hall, etc.)

• Operating room.

• Clean rooms.

• Foodstuff processing factories.

• Local ventilation in kitchens.

•Ventilation of hot exhaust air from equipment rooms, etc.

•Ventilation of humid exhaust air from indoor pools, bathrooms, etc.

• General simple ventilation.

System effect

By changing the balance of the supply fan and exhaust fan’s air volumes, the pressure in the room can be balanced freely, and the interrelation with neighboring spaces can be set freely.

As the room is pressurized, the flow of odors and dust, etc., from neighboring areas can be prevented.

The exhaust air is removed from a local position in the room, and applying an even negative pressure can prevent dispersion of the stale air.

Design and construction

properties

•

An ideal design in which the supply air diffuser and exhaust air outlet position relation and air volume, etc., can be set freely is possible.

•A system which adjusts the temperature and humidity of the supply air diffuser flow to the room environment can be incorporated.

•

The supply and exhaust volume can be set freely according to the changes in conditions.

• The position and shape of the supply air diffuser can be set.

• The temperature and humidity of the supply air diffuser flow can be set accordingly, and dust can be removed as required.

•Effective exhausting of dispersed stale air generation sites is possible from a local exhaust air outlet.

•Ventilation in which the air flow is not felt is possible with the supply air diffuser setting method.

Selection points

• Accurate supply air diffuser can be maintained.

• The room pressure balance can be maintained.

• The supply air diffuser temperature and humidity can be adjusted and dust treatment is possible.

• The pressure is positive.

•

The supply air diffuser temperature and humidity can be adjusted, and dust treatment is possible.

•

The positional relation of the exhaust air outlet to the supply air diffuser is important.

• The room pressure is negative.

•Local exhaust is possible.

•Ventilation without dispersing stale air is possible.

•Ventilation with reduced air flow is possible.

•

The positional relation of the exhaust air outlet to the supply air diffuser is important.

Supply air diffuser

Exhaust fan

Exhaust air outlet

Exhaust fan

Stale air

Fresh outdoor air

CHAPTER 2 ● Air Conditioning System Design Section

3.2.2 Comparison of ventilation methods

There are two main types of ventilation methods.

Centralized ventilation method

This is mainly used in large buildings, with the fresh outdoor air intake being provided within a single equipment room. For this method, primary treatment of the fresh outdoor air, such as heat exchange to the intake air and dust removal is performed before distribution to the building by ducts.

Independent zoned ventilation method

This is mainly used in small to medium sized buildings, where the areas being ventilated use independent devices for fresh outdoor air intake. The rate of use of this method has recently increased as independent control is becoming ever more feasible.

Centralized ventilation method Independent zoned ventilation method

(1) System using Lossnay and cassette-type air conditioner

(2) System using Lossnay and ceiling recessed-type air conditioner

(3) System using OA processing unit

Air intake (Fresh outdoor air)

Exhaust fan

Supply fan

Building use Lossnay

Heat source etc.

Exhaust air (Stale air)

Cassette-type package air conditioner or fan coil unit

Ceiling recessed-type Lossnay

Exhaust air Fresh outdoor air

Finished ceiling

Return grille

Ceiling embedded-type package air conditioner fan coil unit

Ceiling recessed-type Lossnay

Exhaust air Fresh outdoor air

Finished ceiling

Return grille

OA processing unit

CHAPTER 2 ● Air Conditioning System Design Section

3.2.3 Comparison of types of air conditioning systems

Comparison of centralised ventilation method and independent zoned ventilation method

Centralized ventilation method

The air transfer distance is long thus requiring

much fan power.

• Independent equipment room is required.

• Duct space is required.

• Penetration of floors with vertical shaft is not

desired in terms of fire prevention.

Generalized per system.

• Design of outer wall is not lost.

• The indoor supply air diffuser and return grille

can be selected freely for an appropriate design.

As there are many common-use areas, if the

building is a tenant building, an accurate

assessment of operating cost is difficult.

• As the usage time setting and ventilation volume

control, etc., is performed in a central monitoring

room, the user’s needs may not be met

appropriately.

•A large amount of ventilation is required even for

a few persons.

• An ideal supply air diffuser and return grille

position can be selected as the supply air

diffuser and return grilles can be laid out freely.

• The only noise in the room is the aerodynamic

sound.

•

Anti-vibration measures must be taken as the fan

in the equipment room is large.

• Centralized management is easy as it can be

performed in the equipment room.

• The equipment can be inspected at any time.

• Large as the entire system is affected.

• Immediate inspection can be performed in the

equipment room.

Fan power

Installation space

Zoning

Designability

Independent invoicing of

electricity

Controllability

Comfort

Maintenance and

management

Affect of breakdown

Independent zoned ventilation method

As the air transfer distance is short, the fan power

is small.

• Independent equipment room is not required.

• Piping space is required only above the ceiling.

Can be utilised for any one area.

•The number of intakes and exhaust air outlets on

the outer wall will increase; design must be

considered.

• The design will be fixed due to the installation

fittings, so the design of the intakes and exhaust

air outlets must be considered.

Invoicing for each zone separately is possible,

even in a tenant building.

• The user in each zone can operate the ventilator

freely.

• The ventilator can be operated even during off-

peak hours.

• Consideration must be made of the noise from

the main unit.

• Anti-vibration measures are often not required as

the unit is compact and the vibration generated

can be dispersed.

•Work efficiency is poor as the equipment is not

centrally located.

•

An individual unit can be inspected only when the

room it serves is vacant.

• Limited as only independent units are affected.

• Consultation with the tenant is required prior to

inspection of an individual unit.

CHAPTER 2 ● Air Conditioning System Design Section

3.3 Outdoor Air (Ventilation) Load

3.3.1 How to calculate each approximate load

The outdoor air load can be calculated with the following formula if the required outside air intake volume Q m3/h to be introduced is known: (Outdoor air load) = γ · QF · (iO to iR)

= γ [kg/m3] × S [m2] × k × n [person/m2] × Vf [m3/h·person] × (iO to iR): ∆ i [kJ/kg] γ : Specific gravity of air – 1.2 kg/m

S:Building’s airconditioned area k:Thermal coefficient; generally 0.7 to 0.8. n:The average population concentration is the inverse of the occupancy area per person. If the number of

persons in the room is unclear, refer to the Floor space per person table below.

Vf : Outdoor air intake volume per person

Refer to the “Required outdoor air intake volume per person” table shown below. iO : Outdoor air enthalpy – kJ/kg iR : Indoor enthalpy – kJ/kg

Floor space per person table (m

)

(According to the Japan Federation of Architects and Building Engineers Associations)

Department store, shop

Office building

Average Crowded Empty

Restaurant Theatre or cinema hall

General 4 - 7 0.5 - 2 0.5 - 2 5 - 8 1 - 2 0.4 - 0.6

design value 5 3.0 1.0 6.0 1.5 0.5

Required outdoor air intake volume per person table (m3/h·person)

Application example

Required ventilation volume

Degree of smoking

Recommended value Minimum value

Broker’s office

Extremely heavy Newspaper editing room 85 51

Conference room

Quite heavy

Bar

51 42.5

Cabaret

Heavy

Office 25.5 17

Restaurant 25.5 20

Light

Shop

25.5 17

Department store

None

Theatre 25.5 17

Hospital room 34 25.5

Caution

The application of this table to each type of room should be carefully considered in relation to the degree of smoking in the room.

CHAPTER 2 ● Air Conditioning System Design Section

Example calculations of determining ventilation load during both cooling and heating are given as follows:

3.3.2 Ventilation load during cooling (in general office building)

●

Classification of cooling load

Class

Heat from walls (q

WS)

(a) Indoor infiltration heat Heat from glass

from direct sunlight (q

GS)

from conduction & convection (q

GS)

Accumulated heat load in walls (q

SS)

Generated heat from people

Sensible heat (q

HS)

(b) Indoor generated heat

Latent heat (q

HL)

Genarated heat from electrical equipment Sensible heat (q

ES)

Latent heat (q

EL)

RL)

(d) Outdoor air load

Sensible heat (q

FS)

Latent heat (q

FL)

}

(a) is the heat infiltrating the room, and often is 30 to 40% of the entire cooling load.

(b) is the heat generated in the room.

(d) is the heat generated when outdoor air is mixed into part of the supply air diffuser volume and introduced into

the room.

The outdoor air is introduced to provide ventilation for the people in the room, and is referred to as the ventilating load.

Typical load values (during cooling)

Type of load Load

Outdoor air load 53.0 W/m

Indoor

People 26.4 W/m

generated heat

Lighting equipment 30.0 W/m

Indoor infiltration heat 47.6 W/m

Total 157.0 W/m

Conditions: Middle floor of a general office building facing south.

Outdoor air load

33.8%

53.0 W/m

Indoor

infiltration

heat

30.3%

47.6 W/m

Indoor

generated heat

(People, lighting equipment)

35.9%

56.4 W/m

157.0 W/m

●

Determining internal heat gain

When classifying loads, the internal heat gain (indoor generated heat + indoor infiltration heat) will be the value of the outdoor air load subtracted from the approximate cooling load when it is assumed that there is no reheating load.

(Internal heat gain)

= 157.0 W/m2– 53.0 W/m2= 104.0 W/m

This value of internal heat gain is based on assumptions for typical loads. To determine individual levels of internal heat gain, the following is suggested:

CHAPTER 2 ● Air Conditioning System Design Section

Dry bulb temp.

Relative humidity

Wet bulb temp. Enthalpy

Enthalpy difference

Cooling

Outdoor air 33°C 63% 27°C 85 kJ/kg

31.8 kJ/kg

Indoors 26°C 50% 18.7°C 53.2 kJ/kg

When the load per floor area of 1 m2with a ventilation volume of 25 m3/h·person is calculated with the above air conditions, the following is obtained:

Outdoor air (ventilation) load = 1.2 kg/m3(Specific gravity of air) × 0.2 persons/m2(no. of persons per 1 m2)

× 25 m3/h·person (outdoor air volume) × 31.8 kJ/kg (air enthalpy difference indoors/outdoors) × 0.2777 (1,000 W/3,600 sec.) = 53.0 W/m

●

Indoor generated heat

(1) Heat generated from people

Heat generation design value per person in office

Sensible heat (SH) = 63.0 W/person Latent heat (LH) = 69.0 W/person Total heat (TH) = 132.0 W/person The heat generated per 1 m2of floor space is

(Heat generated from people)

= 132.0 W/person × 0.2 person/m2= 26.4 W/m

(2) Heat generated from electrical equipment (lighting)

The approximate value of the room illuminant and power for lighting for a general office with illumination of 300 to 350 Lux, is 20 to 30 W/m2. Note that the heat generated for each watt of electrical power consumption is 1.2 W for fluorescent lights, including the heat generated by the ballast. The following should be considered as the generated heat volume in terms of average of electrical power used for illumination.

(Heat generated by lighting fixtures)

= 25 W/m3× 1.2 W

= 30 W/m

●

Indoor infiltration heat

This is the heat that infiltrates into the building from outside. This can be determined by subtracting the amount of heat generated by people and lighting from the internal heat gain.

(Indoor infiltration heat)

= 104.0 – (26.4 + 30.0) = 47.6 W/m

Cooling load per unit area

When the volume of outdoor air per person is 25 m3/h, and the number of persons per 1 m2is 0.2, the cooling load will be approximately 157.0 W/m2. How these values are determined can be seen as follows:

●

Outdoor air load

Air conditions <Standard design air conditions in Tokyo>

Lossnay recovers approximately 70% of the exhaust air load and saves on approximately 20% of the total load.

Type of load Load

Outdoor air load 56.0 W/m

Internal heat loss 77.7 W/m

Total 133.7 W/m

CHAPTER 2 ● Air Conditioning System Design Section

3.3.3 Ventilation load during heating

●

Classification of heating load

Class

Heat lost from walls (q

WS)

(a)

Indoor heat

Heat lost from glass (q

GS)

loss

Heat loss from conduction & convection (q

GS)

Accumulated heat load in walls (q

SS)

(b)

Outdoor air

Sensible heat (q

FS)

load

Latent heat (q

FL)

During heating, the heat generated by people and electrical equipment in the room can be subtracted from the heating load. However, as the warming up time at the start of heating is short, this generated heat may be ignored in some cases.

Percentage of load

Internal heat loss

In terms of load classification, the internal heat loss is the value of the outdoor air load subtracted from the approximate heating load.

(Internal heat loss)

= 133.7 W/m

– 56.0 W/m2= 77.7 W/m

Heating load per unit area

When the outdoor air volume per person is 25 m3/h, and the number of persons per 1 m2is 0.2 persons, the approximate heating load will be approximately 133.7 W/m2.

●

Outdoor air load

Air conditions <Standard design air conditions in Tokyo>

Conditions: Middle floor of a general office building facing south.

When the load per 1 m2of floor area with a ventilation volume of 25 m3/h·person is calculated with the above air conditions, the following is obtained:

Outdoor air (ventilation) load = 1.2 kg/m3× 0.2 persons/m2× 25 m3/h·person × 33.5 kJ/kg × 0.2777 (1,000 W/3,600 sec.) = 56.0 W/m

Lossnay recovers approximately 70% of the exhaust air load and saves on approximately 30% of the total load.

Outdoor (air

load) air load

41.9%

56.0 W/m

Indoor (heat

loss) heat loss

58.1%

77.7 W/m

133.7 W/m

Dry bulb temp.

Relative humidity

Wet bulb temp. Enthalpy

Enthalpy difference

Heating

Outdoor air 0°C 50% –3°C 5 kJ/kg

33.5 kJ/kg

Indoors 20°C 50% 13.7°C 38.5 kJ/kg

CHAPTER 2 ● Air Conditioning System Design Section

3.4 Ventilation Performance

The ventilation performance is largely affected by the installation conditions. Ample performance may not be achieved unless the model and usage methods are selected according to the conditions. Generally, the ventilation performance is expressed by “Air volume” and “Air flow pressure (static pressure)”, and these are necessary when considering ventilation.

3.4.1 Air volume

Air volume expresses the volume of air exhausted (or supplied) by the unit in a given period. Generally, this is expressed as m3/hr (hour).

3.4.2 Air flow pressure

When a piece of paper is placed in front of a fan and let go, the piece of paper will be blown away. The force that blows the paper away is called the wind pressure (air flow pressure), and this is normally expressed in units of Pa. The air flow pressure is divided into the following three types:

(1) Static pressure

This is the force that presses the surroundings when the air is not moving such as in an automobile tire or rubber balloon. For example, in a water gun, the hydraulic pressure increases when pressed by a piston – and if there is a small hole, the water sprays out with force. The pressure of this water is equivalent to the static pressure for air. The higher the pressure is, the further the water (air) can be sprayed.

(2) Dynamic pressure

This expresses the speed at which air flows, and can be thought of as the force at which a typhoon presses against a building.

(3) Total pressure

This is the total force that air flow has, and is the sum of the static pressure and dynamic pressure.

3.4.3 Measurement of the air volume and air flow pressure

Mitsubishi measures the unit’s air volume and air flow pressure with a device as shown below according to the Japan Industrial Standards (JIS C 9603).

Measuring device (JIS C 9603 standards)

Test machine

Chamber

Static pressure in chamber (Static pressure measurement)

Rectifying net

Wind dispersing plate

Wind gauge duct path

Orifice

Rectifying grid

Auxiliary fan

Throttle device

Pressure difference before and after orifice (Air volume measurement)

CHAPTER 2 ● Air Conditioning System Design Section

Measurement method

The unit is operated with the throttle device fully closed. There is no air flow at this time, and the air volume is 0. The maximum point of the static pressure (A point, the static pressure at this point is called the totally closed pressure) can be obtained. Next, the throttle device is gradually opened, the auxiliary fan is operated, and the middle points (points B, C and D) are obtained. Finally, the throttle device is completely opened, and the auxiliary fan is operated until the static pressure in the chamber reaches 0. The maximum point of the air volume (point E, the air volume at this point is called the fully opened air volume) is obtained. The points are connected as shown below, and are expressed as air volume, static pressure curves (Q-H curve).

Static pressure (

)

Air volume (Q)

CHAPTER 2 ● Air Conditioning System Design Section

4. Characteristics

4.1 How to Read the GUF Series OA Processing Unit Characteristic Curves

4.1.1 Obtaining characteristics from static pressure loss

(1) Static pressure loss from straight pipe duct length (at required air volume) (2) Static pressure loss at curved section (at required air volume) (3) Static pressure loss of related parts (at required air volume)

Total static pressure loss

4.1.2 Calculation of duct pressure loss

When selecting a model that is to be used with a duct, calculate the volumes according to Tables 3, 4, 5 and 6, and then select the unit according to the air volume and static pressure curve.

(2) How to obtain the duct resistivity

Table 4 Circular duct friction loss (steel plate duct,

inner roughness ε = 0.18 mm)

(1) Calculation of a rectangular pipe

Table 3 Conversion table from rectangular pipe to

circular pipe

1234567891011121314151617

100

200

400

600

800

1 000

2 000

4 000

6 000

8 000

10 000

20 000

40 000

60 000

80 000

100 000

200 000

400 000

600 000

800 000

1 00 0000

250

200

350

300

180

160

140

120

d=100cm

d=400cm

d=500cm

2.0

100

V=50m/s

V=50

How to read Table 3

Select the unit as per each duct. In the above example, the ¤520 rectangular pipe only goes as far as 17. Thus, the long side, short side and converted circular pipe values are all multiplied by 100. The point 560 where the two lines cross is hence the value where the rectangular pipe equates to the circular pipe.

How to read Table 4

The point where the line of the circular duct diameter (leftward slanting line) and of the required air velocity (horizontal line) intersect is the pressure loss per 1 m of duct. The value of the slanted line to the lower right of the intersecting point is the average velocity.

Estimated static pressure loss curve obtained from 1 and 2

Long side of

rectangular pipe

Circular pipe diameter

The circular pipe diameter having equal hydraulic radius

Short side of rectangular pipe

Air volume

Static

pressure

4 Intersection with air volume static

pressure characteristic curve

5 Air volume at application point

2 Total static

pressure loss

6 Static pressure loss at

application point

1 Required air

volume

Air volume (m

/h)

Friction loss (Pa/m)

0.1 0.2 0.4 0.60.8 1.0 2.0 4.0 6.0 8.010 20 30 40 5060 80100

Friction loss

0.1 0.2 0.4 0.60.8 1.0 2.0 4.0 6.0 8.010 20 30 40 5060 80100

2.0

5.2

CHAPTER 2 ● Air Conditioning System Design Section

The figure obtained from Table 4 must then be corrected for duct type at various velocities. This can be done using Table 5 below.

Table 5 Friction coefficient compensation table

An alternative, more detailed method for determining the pressure loss in duct work is as shown using the following formula:

Duct inner surface Example

Average velocity (m/sec)

5101520

Very rough surface Concrete finish 1.7 1.8 1.85 1.9

Rough Mortar finish 1.3 1.35 1.35 1.37

Very smooth Drawn steel pipe Vinyl pipe 0.92 0.85 0.82 0.8

Circular pipe section pressure loss

∆p = λ

·· ·

v2(Pa)

∆p = C

··

v2(Pa)

= 0.6 C ·v

λ : Friction resistance coefficient (smooth pipe 0.025) C:Local loss coefficient (refer to Table 6) d:Duct diameter (m)

: Duct length (m)

: Air weight (1.2 kg/m2)

v:Wind velocity (m/s)

CHAPTER 2 ● Air Conditioning System Design Section

(3) How to calculate curved sections

Table 6 List of pressure losses in each duct section

Duct

No.

section

Outline diagram

Conditions

value

R/D = 0.5 0.73 43D

90° =

0.75

0.38 23D

1 Smooth = 1.0 0.26 15D

Elbow = 1.5 0.17 10D

= 2.0 0.15 9D

W/D R/D

0.5 0.5 1.30 79D

0.75 0.47 29D

Rectangular 1.0 0.28 17D

2 Radius 1.5 0.18 11D

Elbow 1-3 0.5 0.95 57D

0.75 0.33 20D

1.0 0.20 12D

1.5 0.13 8D R/D

1 0.5 0.70 42D

Rectangular

0.75 0.16 10D

Vaned

1.0 0.13 8D

Radius

1.5 0.12 7D

Elbow

2 0.5 0.45 27D

0.75 0.12 7D

1.0 0.10 6D

1.5 0.15 9D

90°

4 Miter 0.87 53D

Elbow

Rectangular

Square

1.25 76D

Square Elbow

Rectangular

Vaned

0.35 21D

Square Elbow

Rectangular

Vaned Square Junction

Same loss as circular duct.

Rectangular

Velocity is based on inlet.

Vaned Radius Junction

45°

9 Smooth

Elbow

a = 5° 0.17 10D

10° 0.28 17D 20° 0.45 27D

10 Expansion 30° 0.59 36D

40° 0.73 43D Loss is for hV

1 - hV2

a = 30° 0.02 1D

45° 0.04 2D

11 Contraction 60° 0.07 4D

Loss is for V

Length of

equivalent

circular

pipe

No. of vanes

With or without vanes, rectangular or circular

1/2 times value for similar 90°

Duct

No.

section

Outline diagram

Conditions

value

12 Transformer 0.15 9D

Abrupt

Entrance

0.50 30D

Abrupt

Exit

1.0 60D

Bellmouth

Entrance

0.03 2D

Bellmouth

Exit

1.0 60D

Re-entrant

inlet

0.85 51D

V2 = 0 2.8 170D

0.25 2.4 140D

Sharp edge

0.50 1.9 110D

round orifice

0.75 1.5 90D 1 1.0 60D

Loss is for V

20° 0.02

Pipe inlet

40° 0.03

(with

β 60° 0.05

circular

90° 0.11

hood)

120° 0.20

20° 0.03

Pipe inlet

40° 0.08

(with

β 50° 0.12

rectangular

90° 0.19

hood)

120° 0.27

1/V2 = 0 0.5 30D

0.25 0.45 27D

Abrupt

0.50 0.32 19D

contraction

0.75 0.18 11D

Loss is for V

V1/V2 = 0 1.0 60D

0.20 0.64 39D

Abrupt

0.40 0.36 22D

expansion

0.60 0.16 9D

0.80 0.04 2D Loss is for V

Suction inlet

0.2 35

23 (punched

0.4 7.6

narrow

0.6 3.0

plate)

0.8 1.2

Length of

equivalent

circular

pipe

Free are ratio

14° or less

CHAPTER 2 ● Air Conditioning System Design Section

5. Lossnay Core Effect

5.1 Calculation of the Total Heat Recover Efficiency

The Lossnay Core’s heat recover efficiency can be evaluated using the following three transfer rates:

1) Temperature (sensible heat) recover efficiency

2) Humidity (latent heat) recover efficiency

3) Enthalpy (total heat) recover efficiency

The heat recovery effect can be calculated if two of the above efficiencies is known. (The temperature and enthalpy efficiencies is indicated in the applicable catalogue.)

●

Each recover efficiency can be calculated with the formulas given below.

●

When the supply air volume and exhaust air volume are equal, the heat exchange efficiencies on the supply and exhaust sides are the same.

●

When the supply air volume and exhaust air volume are not equal, the total heat recover efficiency is low if the exhaust volume is lower, and high if the exhaust volume is higher. Refer to the efficiency correction graph in the applicable catalogue for more details.

Item Formula

Temperature heat

exchange ηt =

t (

OA) - t (SA)

× 100

efficiency (%)

t (

OA) - t (

RA)

Enthalpy heat

exchange ηi =

i (

OA) - i (SA)

× 100

efficiency (%)

i (

OA) - i (RA)

η :Efficiency (%) t: Dry bulb temperature (°C) i:Enthalpy (kJ/kg)

Calculation of air conditions after passing through Lossnay Core

If the Lossnay Core heat exchange efficiency and the conditions of the room and outdoor air are known, the conditions of the air entering the room and the air exhausted outdoors can be determined with the following formulas.

When the Lossnay Core efficiency is found using a characteristics graph and if the amount of supply and exhaust air is uneven, the efficiency will be different. In such cases, use the efficiency correction graph.

Supply side Exhaust side

Temperature t

SA = tOA – (tOA – tRA) · ηttEA = tRA + (tOA – tRA) · ηt

Enthalpy i

SA = iOA – (iOA – iRA) · ηiiEA = iRA + (iOA – iRA) · ηi

SA Supply air (Fresh cold or warm air)

RA Return air (Stale cold or warm air)

Indoors Outdoors

EA Exhaust air (Stale air)

OA Outdoor air (Fresh air)

CHAPTER 2 ● Air Conditioning System Design Section

5.2 What is a Psychrometric Chart?

The chart which shows the properties of humid air is called a psychrometric chart. The psychrometric chart can be used to find the (1) Dry bulb temperature, (2) Wet bulb temperature, (3) Absolute humidity, (4) Relative humidity, (5) Dew point and (6) Enthalpy of a certain air condition. If two of these values are known beforehand, the other values can be found with this chart. The way that the air will change when it is heated, cooled, humidified or dehumidified can also be seen easily on the chart.

(1) Dry bulb temperature t (°C)

Generally referred to as standard temperature this is measured with a dry bulb thermometer (conventional thermometer). The obtained value is the dry bulb temperature.

(2) Wet bulb temperature t’ (°C)

When a dry bulb thermometer’s heat sensing section is wrapped in a piece of wet gauze and an ample air flow (3 m/s or more) is applied, the heat applied to the wet bulb by the air and the heat of the water vapor that evaporates from the wet bulb will balance at an equal state. The temperature indicated at this time is called the wet bulb temperature.

(3) Absolute humidity × (kg/kg’)

The weight (kg) of the water vapor that corresponds to the weight (kg’) of the dry air in the humid air is called the absolute humidity.

(4) Relative humidity ϕ (%)

The ratio of the water vapor pressure Pw in the humid air and the water vapor pressure Pws in the saturated air at the same temperature is called the relative humidity. This is obtained with the following formula:

ϕR = PW/PWS × 100

(5) Dew point t” (°C)

The water content in the air will start to condense when air is cooled. The dry bulb temperature at this time is called the dew point.

(6) Enthalpy i (kJ/kg)

Physical matter has a set heat when it is at a certain temperature and state. This retained heat is called the enthalpy, with dry air at 0°C being set at 0.

Temperature (°C)

Absolute humidity × (kg/kg’)

Wet bulb temperature

(dew point) t’ (°C)

Relative humidity ϕ (%)

The dew point t” of the air at point A is the temperature of the point at the same absolute humidity as point A on the saturation curve.

t” °C dew point

Enthalpy i (kJ/kg)

t”

Parallel to absolute temperature scale line

CHAPTER 2 ● Air Conditioning System Design Section

5.3 Calculation of Lossnay Core Heat Recovery

The following figure shows the conditions of various air states when fresh air is introduced through the Lossnay Core. If a sensible heat recovery unit is used alone and is assumed to have the same heat recover efficiency as Lossnay Core, the condition of the air supplied to the room is expressed by point A in the figure. This point shows that the air is very humid in summer and very dry in winter. The air supplied to the room with Lossnay Core is indicated by point S in the figure. The air is precooled and dehumidified in the summer and preheated and humidified in the winter before it is introduced to the room.

iSA

iOA

tOA tSA

iSA

iOA

tRA tRA

SA tOA

XOA

XSA

XRA

XSA

XOA

iRA

The quantity of heat recovered by using the Lossnay Core can be calculated with the following formula.

Total heat recovered: qT = γ · Q · (iOA - iSA) [W]

= γ · Q · (iOA - iRA) × ηi

Where γ = Specific weight of air under standard conditions 1.2 (kg/m3)

Q= Treated air volume (m3/h) t=Temperature (°C) x=Absolute humidity (kg/kg’) i=Enthalpy (kJ/kg) η = Exchange efficiency (%)

●

Suffix meanings

OA : Outdoor air RA : Return air SA : Supply air

Enthalpy (kJ/kg)

Outdoor air load

Lossnay Core heat recovery

Enthalpy (kJ/kg)

Outdoor air load

Lossnay Core heat recovery

Outdoor air

condition in

winter

Supply air condition of

the Lossnay

Supply air condition of

the Lossnay

Room air

condition

in summer

Outdoor air condition

in summer

Absolute

humidity (kg/kg’)

Room air condition in winter

Dry bulb temperature (°C)

CHAPTER 2 ● Air Conditioning System Design Section

iOA

iSA

iRA

tOAtSAtRA

XSA

XRA

5.4 Lossnay Core Heat Recovery Effect

Comparison of outdoor air load of various ventilators

Examples of formulas to compare the heat recovered and outdoor air load when ventilating with the Lossnay (total heat recovery ventirator), sensible heat recovery ventirator and conventional ventilators are shown below.

(1) Cooling during summer

Conditions:

●

Model GUF-100RDH3

●

Heat exchange efficiency table (%) (For summer)

●

Ventilation rate: 1,000 m3/h (Specific gravity of air γ = 1.2 kg/m3)

Lossnay Sensible HRV

Conventional

ventilator

Temperature (sensible heat)

79 75 0

Enthalpy (total heat)

64.5 — 0

●

Lossnay (Supply air diffuser temperature) t

SA = 32°C – (32°C – 27°C) × 0.79 = 28.1°C

(Supply air diffuser enthalpy) i

SA = 86.2 – (86.2 – 55.3) × 0.645 = 66.6 kJ/kg

Heat recovered (86.2 – 66.6) × 1.2 × 1,000 × 0.2777

= 6,532 W

Outdoor air load (66.6 – 55.3) × 1.2 × 1,000 × 0.2777

= 3,766 W

●

Sensible HRV (Supply air diffuser temperature) t

SA = 32°C – (32°C – 27°C) × 0.75 = 28.3°C

(Supply air diffuser enthalpy) i

SA = 82.5 kJ/kg (from psychrometric chart)

Heat recovered (86.2 – 82.5) × 1.2 × 1,000 × 0.2777

= 1,230 W

Outdoor air load (82.5 – 55.3) × 1.2 × 1,000 × 0.2777

= 9,064 W

●

Conventional ventilator If a conventional ventilator is used, the heat recovered will be 0 as the supply air diffuser is equal to the outdoor air. The outdoor air load is: (86.2 – 55.3) × 1.2 × 1,000 × 0.2777

= 10,297 W

Conversion Factor (1,000 W/3,600 sec.)

Calculation example Summer conditions

Supply air

Room air

Air

conditioner

Lossnay Sensible HRV

Conventional

ventilator

Dry bulb temperature

Absolute humidity

Relative humidity

Enthalpy

27°C

28.1 28.3 32

15.0 21.1 21.1

62.8 86.5 70

66.6 82.5 86.2

6,532 1,230 0

3,766 9,064 10,297

37 88 100

11.1 g/kg’

50%

55.3 kJ/kg

Outdoor air

0.0211

Absolute humidity (kg/kg’)

Room air condition in summer

Outdoor air condition

in summer

Supply air condition

of the Lossnay Core

0.0150

0.0111

86.2

66.6

55.3

28.1

Dry bulb temperature (°C)

Lossnay Core heat recovery

Outdoor air load

Enthalpy (kJ/kg)

Exhaust air

Dry bulb temperature Absolute humidity Relative humidity

Enthalpy

32°C

21.1 g/kg’

70%

86.2 kJ/kg

Dry bulb temperature (°C)

Absolute humidity (g/kg’)

Relative humidity (%)

Enthalpy (kJ/kg)

Outdoor air load (W)

Outdoor air load ratio (%)

Total heat recovered (W)

CHAPTER 2 ● Air Conditioning System Design Section

(2) Heating during winter

Conditions:

●

Model GUF-100RDH3

●

Heat exchange efficiency table (%) (For winter)

●

Ventilation rate: 1,000 m3/h (Specific gravity of air γ = 1.2 kg/m3)

Lossnay Sensible HRV

Conventional

ventilator

Temperature (sensible heat)

79 75 0

Enthalpy (total heat)

70 — 0

●

Lossnay (Supply air diffuser temperature) t

(21°C – 0°C) × 0.79+ 0°C = 16.6°C

(Supply air diffuser

enthalpy) iSA = (40.6 – 4.6) × 0.7+ 4.6

= 29.7 kJ/kg

Heat recovered (29.7 – 4.6) × 1.2 × 1,000 × 0.2777

= 8,364 W

Outdoor air load (40.6 – 29.7) × 1.2 × 1,000 × 0.2777

= 3,633 W

●

Sensible HRV (Supply air diffuser temperature) tSA=

(21°C – 0°C) × 0.75+ 0°C = 15.8°C

(Supply air diffuser

enthalpy) iSA = 20.5 kJ/kg

(from psychrometric chart)

Heat recovered (20.5 – 4.6) × 1.2 × 1,000 × 0.2777

= 5,299 W

Outdoor air load (40.6 – 20.5) × 1.2 × 1,000 × 0.2777

= 6,698 W

●

Conventional ventilator If a conventional ventilator is used, the supply air diffuser is the same as the outdoor air and the exhaust is the same as the room air. Thus the heat recovered is 0 kJ/h and the outdoor air load is (40.6 – 4.6) × 1.2 × 1,000 × 0.2777

= 11,997 W

Conversion Factor (1,000 W/3,600 sec.)

Calculation example Winter conditions

iRA

iOA

tOA tSA tRA

XSA

XOA

iSA

Supply air

Room air

Air

conditioner

Lossnay Sensible HRV

Conventional

ventilator

Dry bulb temperature

Absolute humidity

Relative humidity

Enthalpy

21°C

16.6 15.8 0

5.2 1.9 1.9

44.1 17.2 50

29.7 20.5 4.6

8,364 5,299 0

3,633 6,698 11,997

30 56 100

7.7 g/kg’

50%

40.6 kJ/kg

Outdoor air

Exhaust air

Dry bulb temperature Absolute humidity Relative humidity

Enthalpy

0°C

1.9 g/kg’

50%

4.6 kJ/kg

Dry bulb temperature (°C)

Absolute humidity (g/kg’)

Relative humidity (%)

Enthalpy (kJ/kg)

Outdoor air load (W)

Outdoor air load ratio (%)

Total heat recovered (W)

0.0077

Absolute humidity (kg/kg’)

Outdoor air

condition in

winter

Room air condition

in winter

Supply air condition

of the Lossnay Core

0.0051

0.0019

40.6

29.7

4.6

16.6

Dry bulb temperature (°C)

Lossnay Core

heat recovery

Outdoor air load

Enthalpy (kJ/kg)

CHAPTER 2 ● Air Conditioning System Design Section

5.5 Psychrometric chart

Evaporation pressure Pω [kPa]

Absolute humidity χ [kg/kg (DA)]

5.5

5.0

4.5

4.0

3.5

3.0

2.5

2.0

1.5

1.0

0.5

0.1

0.037

0.036

0.035

0.034

0.033

0.96

0.95

0.94

0.93

0.92

Relative capacity ν [m

/kg(DA)]

Saturation level ψ (%)

Relative humidity ψ (%)

Dry bulb temperature t [°C]

Relative enthalpy h [kJ/kg (DA)]

Sensible heat ratio SHF

Heated moisture [kJ/Kg]

Wet air h–x graph (SI)

(-10 to + 50°C, Air pressure 101.325 kPa)

Wet bulb temperature t’ [°C]

0.032

0.031

0.030

0.029

0.028

0.027

0.026

0.025

0.024

0.023

0.022

0.021

0.020

0.019

0.018

0.017

0.016

0.015

0.014

0.013

0.012

0.011

0.010

0.009

0.008

0.007

0.006

0.005

0.004

0.003

0.002

0.001

0.000

0.75

Ice

Water

0.76 0.77 0.78 0.79 0.80 0.81 0.82 0.83 0.84 0.85 0.86 0.87 0.88 0.89 0.90 0.91

0.0

1.0

0.9

0.8

0.7

0.6

0.5

0.4

0.3

u =

CHAPTER 2 ● Air Conditioning System Design Section

6. Humidifying

6.1 The Need for Humidity

Humidity is an important part of air conditioning, especially when heating. During the winter heating months when outside air is drawn in by the ventilator, the low-temperature, low-humidity (absolute humidity) air is heated by the air conditioning unit and this causes a rapid drop in its relative humidity. (For example, 0°C DB, 50%RH outdoor air is introduced and heated as is to 20°C, causing its relative humidity to drop to 13%RH which causes the number of people complaining of dryness to the eyes and throat to increase.) There are also problems such as when the temperature of a room with low humidity is raised, but the people in the room still have cold feet. When the relative humidity is 40% or higher. Since this problem can be corrected by not wastefully raising the temperature, humidity can also play a role in saving energy. (While there are many opinions on what the level of humidity should be for comfort, it is generally believed that 40 to 50%RH relative humidity is suitable for room temperatures of 20 to 24°C. If the humidity is raised higher than this, problems with condensation forming on windows and other areas may occur.)

6.2 Humidity Conditions in Buildings

The humidity conditions in modern buildings is generally quite poor. Even in buildings clearing the building code restrictions with a relative humidity of 40%RH, there are only a few that have good conditions. Buildings with centralized ducts often use spray type humidifiers. With this type of humidifier, the amount of moisture that is dissolved into the air (the amount of effective humidity) is extremely small and as a result the humidity in the room does not rise, making this a serious problem. Moreover, even if humidifiers enabling the air conditioning system to theoretically clear the building codes requirement of 40%RH are incorporated, there are many instances where the following actual causes will change the amount of humidity in a room.

●

The moisture created by people.

Causes that result in

In an office at 21°C, the human body generates a latent heat amount of 171.6 kJ/h “R” and the

an increase in humidity

latent heat for water evaporation is 2,499 kJ/kg. Accordingly, a person will create 171.6/2,499 =

0.686 R/h of water per hour.

●

Water heaters and other such equipment create moisture.

●

Doors being opened and closed and humidity infiltrating through small openings.

●

Absorption of moisture by materials that were abnormally dry at the time of the construction of the building.

●

Increased temperature inside the rooms (Lowers relative humidity).

●

Large amounts of exhaust air.

●

Uneven humidifying by the humidifier in the building or a decline in the amount of humidifying due

Causes that result in to deterioration of the efficiency of the humidifier over time.

a decrease in humidity

●

If the amount of effective humidity (the amount of moisture dissolved into the air) is low. (For example, there are many types of humidifiers available such as high-pressure spray types, ultrasonic types and evaporation-spray types that could be incorporated into an air conditioning system, but as mentioned earlier, if the moisture they emit condenses on the walls of the duct work or if the droplets are not absorbed into the air, it simply becomes water that goes down the drain and contributes nothing towards humidifying the room.)

6.3 Background of the Permeable Film Type Humidifier

Humidifiers can be classified into two main types: spray types and ultrasonic types. However, all things considered, they are not the best overall. The humidifier used in the OA processing unit is a permeable film type that uses natural evaporation to provide clean humidifying. Its merits include its low initial cost, low running cost and uncomplicated operating principle. Its demerits of low humidifying performance and short service life have been overcome by dramatically increasing the evaporating surface of the water without changing the size of the humidifier itself. This is an epoch-making humidifier.

CHAPTER 2 ● Air Conditioning System Design Section

Type

Ultrasonic

type

High-

pressure

spray type

Natural

evaporation

Pan shape

Infrared

type

Dual flow

nozzle type

Electrode

type

Permeable

film type

Operating principle

Humidifying

performance

( /h)

0.4 - 18

2.5 - 300

0.2 - 1.0

0.4 - 35

2.0 - 9.0

1 - 18

0.5 - 78

0.2 - 4.8

Humidifying

efficiency

Medium to

high

Low

High

Medium to

high

High

Responsiveness

(Controlability)

Immediate

Somewhat slow

(Self controlling)

Somewhat slow

Immediate

Somewhat slow

(Self controlling)

Service life

5,000 h

Medium

Vibrator

Long

1,250 h

Short

Evaporator

board

Short

5,000 h

Medium

Infrared

heater

Long

3,000 h Short

to medium

Electrode

plates

12,500 h

or more

(Hard water)

Long

Cost

(5 /h)

High

(130,000)

Low

(30,000)

Low

(70,000)

High

(300,000)

High

(150,000)

High

(500,000)

Special

Power

consumption

(at 5 /h) kW

0.305

0.07

0.01 or less

4.0

5.0

0.75

5.8

0.01 or less

Maintenance

items

Clean oscillator

element every

season. Replace

oscillator element

every 5,000 h.

Replace nozzle

every season.

Clean water tank

every season.

Replace

evaporator board

every season.

Clean water tank

every season.

Replace main

body every 2 to 3

seasons.

Clean water tank

every 3 months.

Replace heater

every 5,000 h.

Replace nozzle

every season.

Clean cylinder

every 2 years.

Replace

electrode plates

every 3 years.

Replace element

every 10 years.

(Hard water)

Running

costs

(Index)

Low to

medium

Low

High

Medium

High

Low

Problem areas

White exhaust

countermeasures

Low humidifying

efficiency.

Countermeasur

es for leakage.

Low humidifying

efficiency.

Short humidifying

element service

life.

Countermeasur

es against

scum.

Improving

maintainability.

High cost.

Improved air

pressure and

water pressure

controllability.

Requires air

compressor.

Improve

maintainability.

High cost.

Water

particles

Oscillator

Water

tank

Electric heater

Infrared

heater

Dry fog

Air

Water

Nozzle

Steam

Solid

electrode

Hot air

Permeable

film sheet

Electric

power

Steam

Water

Heated

water

Supply

(heated) water

6.4 Comparison of Humidifying Methods

Note: Service life is defined as performance up to 80% of the initial performance.

CHAPTER 2 ● Air Conditioning System Design Section

7. Humidifying Effect of the OA Processing Unit

The humidity recovered by the Lossnay Element and the humidity added by the permeable type humidifier provide a humidifying effect that is sufficiently more than the humidity lost in exhaust.

Conditions:●Model GUF-50RDH3

●

Outdoor unit PUHY-P200YGM-A

●

Ventilation 500 m3/h In addition to OA processing, all indoor (Relative air volume γ = 1.2 kg/m3) units are connected for a total of 100%.

Method of Calculation

(1) Finding the air conditions after heating by direct expansion coil

●

Calculate the direct expansion coil performance. Use the correction graph (Refer to page 73) to find the correction coefficient of 0.92 when the outdoor wet bulb temperature is –3°C and the indoor temperature is 20°C. From this, the performance of the direct expansion coil of the OA processing unit is as follows. (6.42 – 2.25) × 0.92 = 3.84 kW

●

Calculate the air conditions after leaving the direct expansion coil. Assuming the fixed pressure ratio of the air is 1.0. There is a temperature increase of 23.0°C. (3.84/1.0/ (1.2 × 500/3,600) = 23.0°C) Due to this temperature increase, the temperature of the air leaving the expansion coil is 38.4°C. (15.4 + 23.0 = 38.4°C)

Since there is no change in absolute humidity from the heating, the absolute humidity leaving the expansion coil is 3.59 g/kg (DA). The rest is taken from the psychrometric chart.

38.4°C 8.6% χ = 3.59 g/kg (DA) i = 47.8 kJ/kg(DA) WB = 17.2°C

Air after humidifying (SA)

Humidified

27.5 38.4

8.04 3.59

35.2 8.6

48.2 47.8

17.2 17.2

1.07 1.07

2.67 0

3.74 1.07

156 45

Not humidified

Dry bulb temperature (°C)

Absolute humidity (g/kg (DA))

Relative humidity (%)

Enthalpy (kJ/kg (DA))

Humidity recovered by Lossnay Element (kg/h)

Humidity added by humidifier (kg/h)

Total amount of humidity (kg/h)

Humidified ratio (*) (%)

* The humidified ratio is expressed as a ratio in

relation to the required humidified amount of the total amount of humidity.

Permeable

film

humidifier

Direct

Expansion

coil

Wet bulb temperature (°C)

Lossnay Core

outlet air (SA)

Dry bulb temperature

Absolute humidity

15.4°C

3.59 g/kg (DA)

33.3%

24.6 kJ/kg (DA)

8.0°C

Relative humidity

Enthalpy

Dry bulb temperature

Absolute humidity

20°C

5.80 g/kg (DA)

40%

35.0 kJ/kg (DA)

Relative humidity

Enthalpy

Wet bulb temperature

Dry bulb temperature

Absolute humidity

0°C

1.80 g/kg (DA)

50%

4.8 kJ/kg (DA)

–3°C

Relative humidity

Enthalpy

Wet bulb temperature

Indoor air (RA)

Exhaust air (EA)

Ventilation amount 500 m

(γ = 1.2 kg/m

)

Outside air (OA)

CHAPTER 2 ● Air Conditioning System Design Section

The humidified amount found is a correction of the rated humidified amount using the above graph, so the following formula is used for calculation. Humidified amount = Rated humidified value × K1 × K2 = 2.7 × 1 × 0.99 = 2.67 kg/h

(2) Finding the amount of humidity added by a permeable film humidifier

1) To find the amount of humidity added by the humidifier, there is a need to correct the rated humidification on the characteristics chart using the amount of air flow and the air conditions at the direct expansion coil outlet.

●

Air flow volume correction: In this case, since the rated air flow is the same as the processed air volume,

the correction coefficient (K1) from Graph 1 will be 1.0.

Graph 1 Air volume change correction

Humidifying volume

correction coefficient

(K1)

Air flow percentage

(Percentage in relation to rated air flow)

0 0.2 0.4 0.6 0.8 1.0 1.2

2.0

1.5

1.0

0.5

01521.5 30

2.0

1.5

1.0

0.5

Rated air flow 1.0 is as follows. GUF-50RDH3 500 m

GUF-100RDH3 1,000 m

Humidifying volume correction

coefficient (K2)

Difference between dry bulb and wet bulb

temperatures of inlet port of the humidifier (K)

●

Air flow volume correction: This is calculated using the difference between dry bulb and wet bulb

temperatures of the direct expansion coil outlet air. It this case, the dry bulb temperature minus the wet bulb temperature is 38.4 – 17.2 = 21.2°C. From Graph 2 it can be seen that the correction coefficient (K2) is 0.99.

Graph 2 Correction graph for heated and humidified Lossnay Core air conditions

●

Percentage in relation to rated air flow = processing air flow/rated air flow

●

The rated air flow is the air flow for the highest speed setting on the characteristics chart for a given model. Example: GUF-50RDH3

......

500 m3/h

CHAPTER 2 ● Air Conditioning System Design Section

2) Method for calculating humidified air conditions

The following is the formula for finding the absolute humidity of humidified air from the amount of humidifying in section 1).

●

Absolute humidity of humidified air = Absolute humidity at Lossnay Core outlet + (Amount of humidifying × 1,000) ÷ (Air density (g) × Processed air amount) (g/kg (DA))

3.59 + (2.67 × 1,000)/(1.2 × 500) = 8.04 (g/kg (DA))

●

If natural evaporation is used, under normal temperatures, a relatively equal wet bulb temperature line can be predicted. Accordingly, the air condition sought will be the intersecting point on the psychrometric chart for the even wet bulb temperature line for the direct expansion coil outlet (17.2°C) and the absolute humidity of humidified air.

27.5°C 35.2% χ = 8.04 g/kg (DA) i = 48.2 kJ/kg (DA) WB = 17.2°C

Dry bulb temperature (°C)

0 15.4 20 27.5 38.4

0.00804

17.2°C

0.00580

0.00359

0.00180 Absolute humidity (kg/kg (DA))

3) Required amount of humidifying and amount of recovered humidity (Recovery ratio)

●

The required amount of humidifying is the amount of humidity added to give both the outside air and the inside air the same amount of absolute humidity. Required amount humidifying = Air density (γ) × Processed air amount × (Indoor absolute temperature – Outdoor absolute humidity)/1,000 R/h (kg/h) = 1.2 × 500 × (5.8 – 1.8)/1,000 = 2.40R/h (kg/h)

●

The amount of humidity recovered is the amount of absolute humidity, in relation to the outside air, contained in the air after humidifying. Accordingly, the following formula is used. Amount of humidity recovered = Air density (γ) × Processed air amount × (Absolute humidity after humidifying – Outdoor absolute humidity)/1,000 R/h (kg/h) = 1.2 × 500 × (8.04 – 1.80)/1,000 = 3.74 kg/h

●

The recovery ratio is the amount of recovered humidity/required amount of humidifying.

3.74/2.40 × 100 = 156%

CHAPTER 2 ● Air Conditioning System Design Section

8. Water Quality and Service Life of Humidifier

8.1 Water Quality Required by Water Supplied to Humidifier

The water supplied to a humidifier should satisfy the following conditions.

●

It should be neutral (pH 5.8 to 8.6).

●

There should be 100 mg/R or less of residual material after evaporation.

●

If the level of residual material after evaporation is high, use a water purifier to adjust the water quality.

8.2 Service Life of Permeable Film Humidifier

The service life of a permeable film humidifier is determined by the amount of accumulation of the residual material in the supply water after evaporation. Results of tests show that the service life of a permeable film humidifier is about five years (6,250 hours) when the water quality has residual material after evaporation of 100 mg/R. The humidifier has reached the end of its service life when the amount of humidification declines to 80% of the its initial amount.

The reason the amount of humidification is reduced over time is due to the residual material after evaporation in the supply water that accumulates on the inside of the permeable film and gradually covers its surface.

8.3 Relationship between Water Quality and Service Life

The service life of a permeable film humidifier is dependent upon the density of the residual material after evaporation.

When residual material after evaporation is 200 mg/R, the service life is approximately 2.5 years. When residual material after evaporation is 400 mg/R, the service life is approximately 1.25 years.

Moreover, if the amount of residual material after evaporation is exceptionally high, the accumulation of it could cause damage the permeable film or cause other such secondary effects. Therefore, water with a high levels of residual material after evaporation cannot offer any positive effect to a permeable film humidifier.

8.4 Water Purifiers

8.4.1 Effect of water purifiers

Even clear, colorless tap water or well water contains components that cannot be seen with the naked eye. The most common of these microscopic components are the “hardness components” of calcium and magnesium. Water that contains a large amount of these hardness components is called hard water and, conversely, water that contains a small amount of these components is called soft water. A water purifier is used to remove calcium and magnesium etc. from the water.

If hard water is used as is, it will cause a build up known as scaling which will reduce flow efficiency and shorten the service life of the equipment. For these reasons, a water purifier should always be used.

8.4.2 Types of water purifiers and their operating principles

The following chart summarizes the representative types of water purifiers.

Operating principle Features Comments

Reverse osmosis Filters the ions from of the In principle, provides effective Requires water pressure. permeable film type supply water. removal of impurities. Low flow volume.

Ion exchange type

Combination of positive and Higher water flow volume than Must be maintained to negative ion exchange plastic. conventional water purifiers. ensure effectiveness.

CHAPTER 2 ● Air Conditioning System Design Section

8.4.3 Difference between a water purifier and a water softener

Do not confuse a water purifier and a water softener. A water softener is a device that softens the water by replacing the calcium, magnesium, and nitrium with sodium, but does not remove impurities from the water. A water purifier, as its name implies, removes all chemical impurities from the water in order to provide pure water (H2O).

8.4.4 Recommended specifications of water purifiers

Reverse Osmosis water purifier is strongly recommended to keep acceptable water quality. The following are one of the recommended specifications, “Cillit-Mini Osmosi MO Series” manufactured by Cillichemie.

Specifications

Note: Water treatment cannot be performed when pressure is less that 3.6 bar.

Piping system incorporating a water purifier (Reference)

To humidifier

Water tank

Solenoid valve

Water purifier

Pump

Elevated water tank

Water supply

Water treatment flow volume m (RR/h)

Model 3.6 bar 6 bar 9 bar

25°C 15°C 25°C 15°C 25°C 15°C

Cillit-Mini Osmosi MO I 4 2.6 5.5 4.2 8.8 6.4

Cillit-Mini Osmosi MO II 5.8 4.4 9.5 7.1 14 10.5 GUF-50RDH3 (2.7 R/h)

Cillit-Mini Osmosi MO III 8 6.2 13 10.8 19 14.5 GUF-100RDH3 (5.4 R/h)

Cillit-Mini Osmosi MO IV 19 14.2 30 25 50 38

CHAPTER 2 ● Air Conditioning System Design Section

9. Dust Removal

9.1 Necessity of Filters

Clean air is necessary for humans to live a comfortable and healthy life. Besides atmospheric pollution that has been generated with the development of modern industries and the growth in the use of automobiles, air pollution in sealed rooms has progressed to the point where it adversely affects the human body, and is now a major problem. Hay fever is most common in the spring and demands for preventing pollen from entering rooms are increasing.

9.2 Data Regarding Dust

The particle diameter of dust and applicable range of filters are shown in Table 1, and representative data regarding outdoor air dust concentrations and indoor dust concentrations is shown in Table 2.

Table 1 Aerosol particle diameters and applicable ranges of various filters

Table 2 Major dust concentrations

Type Reference data

Outdoor air floating dust

Large city 0.1 - 0.15 mg/m

concentration

Small city 0.1 mg/m

or less

Industrial districts 0.2 mg/m

or more

General office 10 mg/h per person

Indoor dust concentration Stores (product vending stores) 5 mg/h per person

Applications with no tobacco smoke 5 mg/h per person

Remarks:

1. The core diameter of outdoor air dust is said to be 2.1 µm.

2. Dust in office rooms is largely caused by smoking, and the core diameter is 0.72 µm. The 14 types of dust (average 0.8 µm) as set by JIS Z 8901 as performance test particles are employed.

3. The core diameter of dust generated in rooms where there is no smoking is approximately the same as outdoor air.

4. Smoking in general offices (as per Japan): Percentage of smokers : Approx. 70% (adult men) Average number of cigarettes : Approx. 1/person·h (including non-smokers) Smoking length of cigarette : Approx. 4 cm Amount of dust generated by one cigarette : Approx. 10 mg/cigarette

Aerosol particle diameter (µm)

Solid particles

Fumes Dust

Mist

Clay

Oil fumes

Tabacco smoke

Carbon black

ZnO fumes

Sea salt particles

Atmospheric

dust

Fine dust, coarse dust fillers

Cement

Pollen

Viruses

Bacteria

Hair

Medium to high efficiency filters

HEPA filter

Coal dust

Fry ashes

Mud Sand

Sprays

Fluid particles

Air filters

Major particles

Aerosol particle

0.001 0.01 0.1 0.3 1 10 100 1000

CHAPTER 2 ● Air Conditioning System Design Section

9.3

Comparison of Dust Collection Efficiency Measurement Methods

The gravitational, colorimetric and counting methods used for measuring dust collection efficiency each have differing features and must be used according to the application of the filter.

Test method Test dust

Inward flow dust Outward flow dust Efficiency

Type of applicable

measurement method measurement method indication method

filters

Synthetic: • Filter passage air AFI • Dust on standard Dust weight volume measured Gravitational

road in Arizona: 72%

measured • Weigh the dust Gravitational ratio Synthetic dust filters

method •

K-1 carbon black: 25%

beforehand remaining on the

• No.7 cotton lint: 3% filter and compare

NBS Degree of Degree of

Comparison of

Electrostatic dust

Colorimetric Atmospheric dust contamination of contamination of

contamination of

percentage of

method white filter paper white filter paper

reduction in degree

(for air conditioning)

of contamination

DOP Diameter of dicoctyl- Electrical counting Absolute filter and Counting phthate small drop measurement using Same as left Counting ratio same type of high method particles: 0.3 µm light aimed at DOP efficiency filter

Synthetic: • Filter passage air

Pre-filter

ASHRAE •

Regulated air cleaner

Dust weight volume measured

Filter for air

Gravitational fine particles: 72% measured • Weigh the dust Gravitational ratio

conditioning

method •

Morocco Black: 23%

beforehand remaining on the

(for coarse dust)

• Cotton linter: 5% filter and compare

ASHRAE Degree of Degree of

Comparison of Filter for air

Colori.etric Atmospheric dust contamination of contamination of

percentage of conditioning (for fine

method white filter paper white filter paper

reduction in degree dust) Electrostatic of contamination dust collector

Air filter test for air

Comparison of

conditioning set by Degree of Degree of

percentage of Filter for air

Japan Air Cleaning JIS 11 types of dust contamination of contamination of

reduction in degree conditioning

Assoc. white filter paper white filter paper

of contamination

(Colorimetric test)

Pre-filter test set • Filter passage air by Japan Air Dust weight volume measured Cleaning Assoc. JIS 8 types of dust measured • Weigh the dust Gravitational ratio Pre-filter (Gravitational beforehand. remaining on the test) filter and compare.

Electrostatic air

Comparison of

cleaning device test Degree of Degree of

percentage of Electrostatic dust

set by Japan Air JIS 11 types of dust contamination of contamination of

reduction in degree collector

Cleaning Assoc. white filter paper white filter paper

of contamination

(Colorimetric test)

CHAPTER 2 ● Air Conditioning System Design Section

Gravitational method

This method is used for air filters which remove coarse dust (10 µm or more). The measurement method is determined by the gravitational ratio of the dust amount on the in-flow side and out-flow sides.

Dust collection ratio =

In-flow side dust amount – Out-flow side dust amount

× 100 (%)

In-flow side dust amount

Colorimetric method

The in-flow side air and out-flow side air are sampled with a suction pump and passed though filtering paper. The sampled air is adjusted so that the degree of contamination on both filter papers is the same, and the results are determined by the sampled air volume ratios on both sides.

Dust collection ratio =

Out-flow side sampling amount – In-flow side sampling amount

× 100 (%)

Out-flow side sampling amount

Orifice

Dust supply device

Manometer

Motor

Dust container

Mixing blades

Dust supply outlet

Unit (mm)

Rectifying grid

Air volume adjustment plate

Air-feed fan

Window

Specimen

Performance test device Example of dust supply device

Passed dust

collection filter

Air-feed fan

Orifice

Square duct

Throttle device

Rectifying grid

Venturi pipe

Dust chamber

Air filter

Specimen

3.5D3D 2D 2L 2L

Baffle plate

Coupling pipe

7° or less

Pressure loss concentration measurement position

Coupling pipe

Rectifying grid

Coupling

pipe

Round duct

CHAPTER 2 ● Air Conditioning System Design Section

Model Cooling capacity Heating capacity

Outdoor

Filter efficiency

air amount

processing GUF-50RDH3 + High-

65%

unit efficiency filter 5.18 kW 5.84 kW 500 m

(Colorimetric method)

PZ-50RFM 1 unit

Model

Cooling Heating Air flow

Filter efficiency

performance performance volume

Indoor unit

PLFY-P40VKM-A + Highefficiency filter 4.5 kW 5.0 kW 15 m3/min 65% (Colorimetric method) PAC-SE13KF-E 2 units

In a system such as this where the performance of each component is already known and the indoor dust density is being sought, there may be times when the indoor filter performance is calculated for use as the allocated value for indoor dust density. In such cases, the following formula is used.

Ci =

G + CoQo (1 –

Qo + Qi ηi

i =

G + C

o Qo (1 – ηo) – Ci Qo

× 100

Ci Qi

Example of calculation

In the illustration above, the indoor dust density for the following design conditions is found as follows.

Outline of air conditioning

9.4 Calculating Dust Density

The following is an air conditioning system using an OA processing unit.

Dust density detection

Qo : Outdoor air intake amount (m3/h) Q

i : Indoor unit air flow amount (m

/h)

(Total air flow amount for indoor unit)

o :

High-efficiency filter dust removal ratio (%) (Colorimetric method)

ηi : Indoor unit filter dust removal ratio (%) (Colorimetric method)

o : Outside air airborne dust density (mg/m

)

i : Indoor dust density (mg/m

)

G: Amount of dust generated indoors (mg/h)

Air conditioning area Number of people in room

Amount of outdoor air used Cooling capacity Heating capacity

100 m

(Office) 20 people 25 m3/h·people × 20 people = 500 m3/h 14.18 W 15.84 W

Unit used

Indoor unit

OA processing unit

High-efficiency filter ηo

Indoor unit filter ηi

Calculation

......

Outdoor air intake amount Qo = 500 m3/h Indoor unit air flow amount Qi = 15 × 2 × 60 = 1,800 m3/h High-efficiency filter – dust removal ratio ηo = 65% (ηo’ = 67% Particle diameter 2.1 µm*) Indoor unit filter – dust removal ratio ηi=65% (ηi’ = 57% Particle diameter 0.72 µm*) Outside air airborne dust density Co = 0.1 mg/m

Amount of dust generated indoors G = Amount of dust created per person × Number

of people in room

= 10 mg/h·person × 20 people = 200 mg/h

From the above, the following shows the calculation for indoor dust density Ci.

Ci =

200 + 0.1 × 500 (1 – 0.65)

0.130 mg/m3( 0.142 mg/m3*)

500 + 1,800 × 0.65

The result clears the dust density of 0.15 mg/m3set by building codes and other such ordinances. Conversely, the dust removal ratio for the indoor filter for attaining the indoor dust density Ci of 0.15 mg/m3is calculated as follows.

i =

200 + 0.1 × 500 (1 – 0.65) – 0.15 × 500

× 100 52.7% ( 52.4%*)

0.15 × 1,800

This shows that a filter for the indoor unit with a minimum dust removal ratio of 52.7% (Colorimetric method) is required.

* The result of a calculation using an average outdoor airborne particle diameter of 2.1 µm and an average indoor

airborne particle diameter of 0.72 µm is shown.

CHAPTER 2 ● Air Conditioning System Design Section

{}

CHAPTER 2 ● Air Conditioning System Design Section

10. Sound

Sound is emitted when any object is excited causing it to vibrate. The object that vibrates is called the sound source, and the energy that is generated at the source is transmitted through the air to the human ear. Humans can hear the sound only when the ear drum vibrates.

10.1 Sound level and auditory perception

Sound level is the sound wave energy that passes through a unit area in a unit time, and is expressed in dB (decibel) units. The sound heard by the human ear differs according to the strength of the sound and the frequency, and the relation to the pure tone sound is as shown on the right. The vertical line shows the strength of the sound and the horizontal line shows the frequency. For frequencies between 20 Hz to 15,000 Hz which can be felt by the human ear, the strength of sound that can be felt that is equivalent to a 1,000 Hz sound is obtained for each frequency. The point where these points cross is the sound level curve, and a sound pressure level numerical value of 1,000 Hz is expressed. These are called units of phons. For example, the point on the 60 curve is perceived as 60 phons.

●

On average, the human senses a sound that is less than 1,000 Hz as rather weak, and a sound between 2,000 to 5,000 Hz as strong.

10.2 How to measure sound levels

A sound level meter (JIS C 1502, IEC 651) is used to measure sound levels. This sound level meter has three characteristics (A, B and C characteristics) as shown on the right. These represent various sound wave characteristics. Generally, the A characteristic, which is the most similar to the human ear, is used.

Sound level (dB)

Frequency (Hz)

Minimum audible valve

120 dB

100

–20

–2

–0.2

–0.02

–0.002

–0.0002

–0.00002

4.2

Response (dB)

Frequency (Hz)

C characteristic

B characteristic

A characteristic

Sound

(Pa)

Sound

strength

(W / cm

)

ISO audio perception curve

CHAPTER 2 ● Air Conditioning System Design Section

Room application dB NC value Room application dB NC value

Broadcasting studio 25 15 - 20 Cinema 40 30

Music hall 30 20 Hospital 35 30

Theatre (approx. 500 seats) 35 20 - 25 Library 40 30

Classroom 40 25 Small office 45 30 - 35

Conference room 40 25 Restaurant 50 45

Apartment 40 25 - 30 Gymnasium 55 50

Hotel 40 25 - 30 Large conference room 50 45

Housing (room) 40 25 - 30 Factory 70 50 or more

10.3 Frequency analysis of sound

It is said that the human ear senses differently according to the frequency. However, the sound generated from a vibration is not limited to one frequency, but instead, various frequencies are generated at differing levels. This is expressed by the NC curve, which is determined according to the difficulty of hearing a conversation.

●

Even if the sound is a very low level, it is annoying if a specific frequency is emitted very loudly. These sounds are suppressed to a minimum during product design stages, but, the sound may become very disturbing with resonance of the ceiling, wall, etc.

Example Continuous frequency analysis NC curve

●

Tolerable noise levels and NC values according to room application

Frequency band (Hz)

Level (dB)

Frequency (Hz)

SPL (dB)

Min. audible limit

CHAPTER 2 ● Air Conditioning System Design Section

10.4 Indoor noise

(1) Principle of indoor noise

1) Power levels

The Power level (PWL) of the sound source must be understood when considering noise effects. The following formula is used to obtain PWL from the measured sound pressure data (values noted in catalog) in an anechoic chamber.

PWL = SPLo + 20 logro + 11 [dB]................................(I)

PWL : Sound source power level (dB)

SPLo : Measured sound pressure in anechoic

chamber (dB)

ro : Measurement distance (m)

2) Principal model

Consider the room shown in Figs. 1 and 2.

●

Fig. 1 shows an example of the integrated main unit and supply air diffuser (and return grille). Fig. 2 shows an example of a separated main unit and supply air diffuser (and return grille).

●

is the direct sound from the supply air diffuser (return grille) and is the echo sound. ( to ) is the direct sound that is emitted from the main unit and duct and passes through the finished ceiling and leaks. is the echo sound of .

3) Setting of noise

●

The following formula is used to obtain the noise value at a position in the room.

SPL [dB] = PWL + 10 log + ................(II)

(i) (ii)

SPL :

Sound pressure level at reception point [dB]

PWL : Sound source power level [dB]

Q:Directivity factor (Refer to Fig. 3)

r:Distance from sound source [m]

R:Room constant [R – αS/(1 – α)]

α :Average sound absorption ratio in room

(Normally, 0.1 to 0.2)

S:Total surface area in room [m2]

Sound source position

Centre of room

Centre of ceiling

Edge

Corner

Fig. 1

Fig. 2

Fig. 3 (Sound source position and directivity

factor Q)

4πr

{}

Main unit

Supply air diffuser (return grille)

Main unit

CHAPTER 2 ● Air Conditioning System Design Section

●

For the supply air diffuser (and return grille) in Fig. 2, PWL must be corrected for the noise alternation provided by the duct work (TL) such that:

PWL’ = PWL – TL

●

Item (i) in formula (II) is the direct sound ( , ), and (ii) is the echo sound ( , ).

●

The number of sound sources in the room (main unit, supply air diffuser, return grille etc.) is obtained by calculating formula (II), and combining the number with formula (III).

SPL = 10log (10

SPL1/10

+ 10

SPL2/10

)

........................

(III)

●

The average sound absorption rate in the room and the ceiling transmission loss differ according to the frequency, so formula (II) is calculated for each frequwncy band, and is combined with formula (III) for an accurate value.

(2) Avoiding noise disturbance from

OA processing unit

1) When unit air passage behind ceiling is sound source (Fig. 1 , , Fig. 2 to , )

(A) Avoid the following types of design when disturbing

noise may be emitted from large units. (Refer to Fig. 4) a) Sudden contraction of duct diameter

(Ex. ø 250 → ø 150, ø 200 → ø 100)

b) Sudden curves in aluminum flexible ducts, etc.

(Especially right after unit outlet) c) Opening in ceiling plates d) Suspension on weak material

(B) The following countermeasures should be taken.

(Refer to Fig. 5) a) Use ceiling material with high soundproofing

properties (high transmission loss). (Care is

required for low frequency components as the

difference in material is great). b) Addition of soundproofing material to areas

below sound source.

(The entire surface must be covered when

using soundproofing sheets. Note, that in some

cases, covering of the area around the unit

may not be possible due to the heat generated

from the unit.)

125

250

500

1,000

2,000

4,000

Material ( )

indicates

thickness (mm)

Lauan

plywood (12)

—

Fig. 4

Fig. 5

Transmission loss in ceiling material (dB) Example

Average

Plaster

board (7)

Plaster

board (9)

Frequency band (Hz)

a) d)

a) b)

c) b)

CHAPTER 2 ● Air Conditioning System Design Section

When supply air diffuser (and return grille) is sound source

..... part 1

(A) If the main unit is separated from the supply air

diffuser (and return grille) as shown in Fig. 6, the use of a silencer box a), silence duct b) or silence grille c) is recommended.

(B) If a draft sound is being emitted from the supply air

diffuser (and return grille), branch the flow as shown in Fig. 7 a), lower the flow velocity with a grille, and add a silencer duct to section b). (If the length is the same, a silencer duct with the small diameter is more effective.)

When supply air diffuser (and return grille) is sound source

..... part 2

(A) If the main unit and supply air diffuser (and return

grille) are integrated as shown in Fig. 8, or if the measures taken in 2) a) and b) are inadequate, the interior material in the room can be changed to that having a high sound absorbency as shown in Fig. 8 a). This is not, however, very effective towards direct sounds.

(B) Installing the sound source in the corner of the

room as shown in Fig. 8 b) is effective towards the center of the room, but will be inadequate towards people in the corner of the room.

Fig. 6

Fig. 7

Fig. 8

a) b) c)

a) b)

CHAPTER 2 ● Air Conditioning System Design Section

11. Precautions when Using

11.1 OA Processing Unit Usage Conditions

Model Installation conditions for main unit

Supply air diffuser conditions

Exhaust air conditions

GUF-50RDH3 GUF-100RDH3

1 *2

0°C to +40°C, relative –15°C to +40°C, relative –10°C to +40°C, relative GUF-50RD3 humidity of 80% or less humidity of 80% or less humidity of 80% or less GUF-100RD3

Note: *1 However, this for a room in a common residential building and with conditions for air conditioning

temperature and humidity. Accordingly, if an item with a large temperature difference such as a large refrigerator is used, this model cannot be used even if it falls within the values shown above.

Depending on the usage conditions of the outdoor unit, there may be cases when it may not be capable of using an supply air diffuser to –15°C. Therefore, always check the usage conditions of the outdoor unit.

11.1.1 Use in cold climates (outdoor temperature: –5°C or less)

Plot the OA processing unit intake air conditions A and B on a psychrometric chart as shown on the right. If the high temperature side air B intersects the saturation curve such as at C, moisture condensation or frosting will occur on the Lossnay Core. In this case, the low temperature side air A should be preheated to the temperature indicated by point A’ so that point C shifts to the point C’.

●

The OA processing unit cannot be used where toxic gases and corrosive elements such as acids, alkalis, organic solvents, oil mist or paints exist.

●

Use where heat is recovered from odor-laden air and supplied to another place (area) is not possible.

●

Avoid use where salt or hot water damage may occur.

●

Pre-heating is necessary if using the system in a cold climate (locations where winter temperatures are below -15

°C).

11.1.2 Use in other special conditions

A’

C’

Saturation curve

Dry bulb temperature (°C)

Absolute humidity (kg/kg’)

CHAPTER 2 ● Air Conditioning System Design Section

11.2 Noise Value of OA Processing Unit

The noise level specified for OA processing units is as that measured in an anechoic chamber. The sound level may increase according to the installation construction material, and room contents. When using the OA processing unit in a quiet room, it is recommended that measures such as installing a muffling duct. Note: Please consult with nearest OA processing unit supplier about availability of these parts.

11.3 Duct Design

●

Always treat the two ducts on the outdoor side (outdoor air intake and exhaust outlet) with insulation to prevent frosting or condensation.

●

Always install heat insulation to prevent condensation on the supply air diffuser duct (system section material) as well. (Heating and humidifying units only.)

●

The outdoor duct gradient must be 1/30 or more (to wall side) to prevent rain water from infiltrating the system.

●

Do not use the standard vent caps or round hoods where they may come into direct contact with rain water.

11.4 OA Processing Unit with Humidifier

●

In areas where freezing is anticipated, take steps to prevent the water supply pipes from freezing.

●

Always provide a gradient of 1/100 or more for the drain pipe.

●

Take steps to prevent condensation on the water supply and drain pipes.

●

Makes sure that the water supply to the humidifier is 40°C or less.

11.5 Transmission Rate of Various Gases and Related Maximum Workplace Concentration

Measurement

Air volume Exhaust air

Supply air diffuser

Transmission

Max. workplace

conditions

Gas name ratio concentration

concentration

rate

concentrations

QSA/QRA CRA (ppm) CSA (ppm) (%) (ppm)

Hydrogen fluoride 1.0 36 <0.5 –0 0.6

Exhaust

air t = 24°C Hydrogen chloride 1.0 42 <0.5 –0 5

Nitric acid 1.0 20 <0.5 –0 10

Supply air t = 30°C Sulfulic acid 1.0 2.6 mg/m

–0 mg/m

–0 0.25 Measurement Trichlene 1.0 85.1 3.7 4.3 200 method

Acetone

1.0 3.3 0.15 4.5 1,000

•

Gas detection pipe

1.5 20.4 0.54 2.6

for HF, HCI, HNO

3 0.5 5.9 0.14 2.4

Xylene 1.0 5.9 0.5 8.5 150

• Chemical analysis 1.5 4.9 0.48 9.8 with colorimetric 0.5 38.4 0.17 0.4 method for H

2SO4 Isopropyl alcohol 1.0 44.7 2.0 4.5 400

1.5 31.0 2.6 8.4

• Gas Methanol 1.0 34.4 1.5 4.4 200 chromatography Ethanol 1.0 32.7 1.6 4.9 1,000 for organic

Ethyl acetate

0.5 3.3 0 0

solvents,etc.

alcohol

1.0 21.7 0.83 3.8 400

1.5 26.3 1.39 5.3 The fans are Ammonia 1.0 75.0 21 28 50 positioned at the Hydrogen sulfide 1.0 1.5 0.1 6.7 10 supply air exhaust Carbon monoxide 1.0 50 0.5 1 suction positions of Carbon dioxide 1.0 5,000 100 2 the element Smoke 1.0 1 - 2

Formaldehyde 1.0 0.5 0.01 2 0.08

CHAPTER 2 ● Air Conditioning System Design Section

Note:●Water soluble gases and mists cannot be used because the amount that is transmitted with the water is

too great.

●

Acidic gases and mists cannot be used because these will accumulate in the element and cause damage.

: OK : Caution should be used

× : Should not be used

Main

Molecular

Gas Non-toxic/ Sulubility

Max.

Useability

generation Gas name

formula

vapour toxic/ in water workplace of Lossnay

site mist odor

m /m

g/100g

concentration Core

Sulfuric acid H

2SO

4 Mist Found 2,380 0.25

Nitric acid HNO

3 Mist Found 180 10

Phosphoric acid H

3PO

4 Mist Found 41 0.1

Acetic acid CH

3COOH Mist Bad odor 2,115 25

Chemical

Hydrogen chloride HCl Gas Found 427 58 5

plantor

Hydrogen fluoride HF Gas Found 90 0.6

chemical

Sulfur dioxide SO

2 Gas Found 32.8 0.25

laboratory

Hydrogen sulfide H2S Gas Found 2.3 10

Ammonia NH

3 Gas Bad odor 635 40 50

Phosphine PH

3 Gas Found 0.26 0.1

Methanol CH3OH Vapor Found Soluble 200

Ethanol CH

3CH2OH Vapor Found Soluble 1,000

Ketone Vapor Found Soluble 1,000

Skatole C

9H9N Gas Bad odor Minute

Toilet Ammonia NH

3 Gas Bad odor 635 40 50

Indole C9H7N Gas Bad odor Minute

Nitric monoxide NO 0.0043 50

Others

Ozone O

3 0.00139 0.1

Methane CH

4 0.0301

Chlorine Cl

2 Minute 0.5

Air Mixed gases Gas None 0.0167

Air

Oxygen O

2 Gas None 0.0283

(reference)

Nitrogen N

2 Gas None 0.0143

Carbon monoxide CO Gas Found 0.0214

Carbon dioxide CO

2 Gas None 0.759

11.6 Solubility of Odors and Toxic Gases, etc., in Water and Effect on Lossnay Core

CHAPTER 3

Control System

Design Section

CHAPTER 3 ● Control System Design Section

OA processing unit fan operation when indoor unit is stopped

OA processing unit stopping when indoor unit is operated

Switching OA processing unit fan speed

Ventilation mode Auto

Humidifier (Only GUF-50/100RDH3) Auto (When heating)

Filter maintenance indicator (Optional setting)

OA processing unit error indicator

The sum of indoor units setting for one OA

16 units max

processing unit

The sum of interlocked OA processing units

1 unit

setting for one indoor unit

Start/Stop

Fan speed switching

Ventilation mode Auto

Humidifier (Only GUF-50/100RDH3) Auto (When heating)

Filter maintenance indicator (Optional setting)

OA processing unit error indicator

The sum of OA processing unit registering in

16 units max

one group

The sum of remote controllers and centralized

controllers registering to one OA processing 5 units max (Note)

unit

1. System Selection

Interlocked with indoor units

Non-interlocked OA processing units

TB3

Outdoor

unit

M-NET transmission line

MA Remote

controller

MA Remote

controller

cannot be used.

Indoor unit

OA processing

unit

Outdoor

unit

MA Remote

controller

OA processing

unit

OA processing

unit

OA processing

unit

Outdoor

unit

Group 1 Group 2

Connecting MA Remote controler and OA Processing Units

Group 3

OA processing

unit (IC Mode)

00 OA processing unit (IC Mode)

MA Remote

controler

MA Remote

controler

MA Remote

controler

MA Remote

controler

Note: Number of local remote controller is 2 units max.

Group 1 : Multiple OA processing units (IC mode) only. Group 2 : One OA processing unit (IC) and two Remote controllers. Group 3 : One OA processing unit (IC) only.

Caution

●

The addresses of the entire system are set automatically so make sure the address of each unit is initially set at 00 (setting at time of delivery).

●

When indoor units are not interlocked with OA processing units switch the setting to IC mode (DIP-SW3-1 to ON).

●

When connecting two MA Remote controlers the same group be sure to set one as the sub-remote.

●

You cannot use both M-NET remotes and MA Remote controlers with OA procesesing units in the same group.

●

You cannot connect more than three Remote controlers to OA processing units in the same group.

TB3

CHAPTER 3 ● Control System Design Section

Central

Controller

System

TB7 TB3

Central controller system

Outdoor unit

Centralized

controller

MA Remote controller MA Remote controller

MA Remote controller

MA Remote

controller

MA Remote

controller

MA Remote

controller

Power supply unit

PAC-SC34KUA

Indoor unit

OA processing

unit

OA processing

unit

OA processing

unit

OA processing

unit

OA processing unit

CHAPTER 3 ● Control System Design Section

1.1 System Designs. Example 1

Indoor units and OA processing unit interlocked system

Features

●

Interlocked operation with indoor units is possible.

●

Can also perform independent OA processing unit operations using MA/ME Remote controller.

System examples

The following groups can be configured.

Single refrigerant system

(

002

)

(

003

)(

004

)

(

005

)

(

006

)

(

007

)

(

008

)

(

009

)

(

010

)(

001

)

(

051

)

Group 1 : Group of one indoor unit and one OA processing unit in interlocked operation. Group 2 : Group of multiple indoor units and one OA processing unit in interlocked operation. Group 3 : Group of one indoor unit with two remote controllers and one OA processing unit in interlocked operation. Group 4, 5 : Group of multiple groups and one OA processing unit in interlocked operation.

Group 1 : Group of one indoor unit and one OA processing unit in interlocked operation. Group 2 : Group of multiple indoor units (with different refrigerants) and one OA processing unit in interlocked operation. Group 3 : Group of multiple indoor units (with same refrigerant) and one OA processing unit in interlocked operation.

(

051

) (

055

)

(

002

)

(

001

)(

003

)

(

004

)

(

005

)(

006

)(

007

)

(

008

)

Outdoor unit

( ) address

Indoor unit

Group 1

Group 2 Group 3 Group 4 Group 5

MA Remote controller

MA Remote controller MA Remote controller

MA Remote controller

OA processing

unit

Outdoor unit Outdoor unit

Refrigerant 1 Refrigerant 2

Indoor

unit

Indoor

unit

Indoor unit

Indoor

unit

Group 1 Group 2

Group 3

MA Remote controller MA Remote controller MA Remote controller

OA processing

unit

OA processing

unit

OA processing

unit

Indoor

unit

Indoor unit

Indoor

unit

Indoor

unit

Indoor

unit

OA processing

unit

OA processing

unit

OA processing

unit

Multiple refrigerant system

(Main) (Sub)

Local remote MELANS Series

MA Remote ME Remote Simple remote Group remote System remote Centralized Centralized

Model

controller controller controller controller controller controller controller

PAR-20MAA PAR-F27MEA

PAC-SE51CRA

PAC-SC30GRA PAC-SF41SCA

MJ-103MTRA

MJ-180A

or PAC-YT51CRA or G-50A

No. of controlable (Groups/Units)

1 Group/16 Units 1 Group/16 Units 1 Group/16 Units 8 Groups/16 Units

32 Groups/50 Units 50 Groups/50 Units

100 Groups/100 Units

200 Groups/200 Units

Start/Stop

Fan speed switching ×××

Ventilation mode switching ЧЧЧЧЧЧЧ

Humidifier switching

*1 *1 *1 *1 *1 *1 *1

(Only GUF-50/100RDH3)

Operation mode switching *2 *2 × *2 *2 *2 *2

Temperature setting *3 *3 *3 *3 *3 *3 *3

Priority instructions.

×××× ×

Local permitted/Prohibited

Status (Operation/Stop) × ×

Fan speed switching ×××

Ventilation mode ЧЧЧЧЧЧЧ

Humidifier (Only GUF-50/100RDH3)

× *4 × *4 × *4 × *4 × *4 × *4 × *4

Operation mode

Setting temperature *3 *3 *3 *3 *3 *3 *3

Error

Error contents

Filter sign ×

Local permitted/Prohibited

Weekly ЧЧЧЧЧ

Stop/Starts per day 2 2 ×××36

Stop/Starts per week ЧЧЧЧЧ21 42

Minumum setting (minutes)

10 10 ×××10 1

Error record ЧЧЧЧЧ

Switched & display : Group/Batch : Group only (or function available) × : Not available

CHAPTER 3 ● Control System Design Section

OA Processing unit function table (Interlocked settings)

Item Details

The sum of indoor units setting for one OA processing unit 16 units max The sum of interlocked OA processing units setting for one indoor unit

1 unit Independent Start/Stop of ventilation (OA processing unit) Possible Fan speed switching High/Low Ventilation mode switching Auto Humidifier switching (Only GUF-50/100RDH3) Possible (When indoor unit is heating) Operation mode switching Heat/Cool/Fan (Follows the operation mode of indoor unit) Filter maintenance indicator (Optional setting) 3,000 h/1,500 h/4,500 h/No display Error Display

•To operate OA processing units and indoor units by interlocking, it is necessary to perform interlock setting from a remote controller.

• OA processing unit cannot be interlocked to another one.

• OA processing units set to group registration (non-interlocked) cannot be interlocked setting.

Restrictions and precautions

•

When the OA processing unit is interlocked setting, set the OA processing unit DIP switch 3-1 to off.

•

The OA processing unit will operate in the same mode as the synchronized indoor unit (heat, cool and fan). (The OA processing unit will be cool when the indoor unit is operated in dry mode.)

•

To connect two MA Remote controllers to the same group, set one MA Remote controller as a subremote controller.

•

MA Remote controllers and other local remote controllers cannot be used together in the same group.

Controller function table especially regarded to the OA processing unit

OperationMonitoring

Scheduling/

Recording

Note: *1 When indoor unit is heating, interlocked OA processing unit is operating humidifier.

*2 The OA processing unit will operate in the same mode as the synchronized indoor unit (heat, cool and fan).

(The OA processing unit will be cool when the indoor unit is operated in dry mode.) When using with multiple indoor units that are set differently, the OA processing unit will operate in the mode with priority of:

heat, cool and fan. *3 In the case of GUF-50/100RDH3, temperature setting in heat mode is set at the OA processing unit DIP switch. *4 When the “Heating” is displayed on the controller, the humidifier is also operating.

CHAPTER 3 ● Control System Design Section

1.2 System Designs. Example 2

Non-interlocked OA processing unit system with remote controller

Features

●

Local remote controller can operate and monitor each group of OA processing units.

System example

The following groups can be configured.

Single refrigerant system

Group 1,2 : Groups of multiple OA processing units. Group 3 : Group of multiple OA processing units with two remote controllers.

(

000

)(

000

)(

000

)(

000

)(

000

)(

000

)(

000

)

(

000

)

Outdoor unit

( ) address

Group 1

Group 2

Group 3

MA Remote controller MA Remote controller MA Remote controller

OA processing

unit

OA processing

unit

OA processing

unit

OA processing

unit

Note: On OA processing unit for a non-interlocked OA processing unit group, set DIP switch 3-1 (synchronous air

conditioning switch) to on. Address setting is not required for a single refrigerant system (only when no M-NET remote controllers and MELANS are used). (Keep the factory set address (000) for both the outdoor unit and the OA processing units.)

Multiple refrigerant system

Group 1,3 : Groups of multiple OA processing units. Group 2 : Group of multiple OA processing units (with different refrigerants).

(

051

) (

055

)

(

002

)

(

001

)(

004

)(

003

) (

008

)(

007

)(

006

)(

005

)

Outdoor unit

Refrigerant 1 Refrigerant 2

( ) address

Group 1 Group 2 Group 3

MA Remote controller MA Remote controller MA Remote controller

OA processing

unit

OA processing

unit

OA processing unit

OA processing

unit

OA processing

unit

Note: On OA processing unit for a non-interlocked OA processing unit group, set DIP switch 3-1 (synchronous air

conditioning switch) to on

Local remote MELANS Series

Model

MA Remote ME Remote Simple remote Group remote System remote Centralized Centralized

controller controller controller controller controller controller controller

PAR-20MAA PAR-F27MEA

PAC-SE51CRA

PAC-SC30GRA PAC-SF41SCA

MJ-103MTRA

MJ-180A

or PAC-YT51CRA or G-50A

No. of controlable (Groups/Units) 1 Group/16 Units 1 Group/16 Units 1 Group/16 Units 8 Groups/16 Units

32 Groups/50 Units 50 Groups/50 Units

100 Groups/100 Units

200 Groups/200 Units

Start/Stop

Fan speed switching ×

Ventilation mode switching ЧЧЧЧЧЧЧ

Humidifier switching

*1 *1 *1 *1 *1 *1 *1

(Only GUF-50/100RDH3)

Operation mode switching *3 *3 × *4 *4 *4 *4

Temperature setting

Priority instructions.

××××

Local permitted/Prohibited

Status (Operation/Stop)

Fan speed switching ×

Ventilation mode ЧЧЧЧЧЧЧ

Humidifier (Only GUF-50/100RDH3)

× *2 × *2 × *2 × *2 × *2 × *2 × *2

Operation mode ×

Setting temperature

Error

Error contents

Filter sign ×

Local permitted/Prohibited

Weekly ЧЧЧЧЧ

Stop/Starts per day 2 2 ×××36

Stop/Starts per week ЧЧЧЧЧ21 42

Minumum setting (minutes)

10 10 ×××10 1

Error record ××× ×

Switched & display : Group/Batch : Group only (or function available) × : Not available

CHAPTER 3 ● Control System Design Section

OA Processing unit function table (Group settings)

Controller function table

Item Details

The sum of remote controllers and/or MELANS units that can be 5 units max connected to one OA processing unit (Number of local remote controller is 2 units max.) Operation of two remote controllers in one group Possible Fan speed switching High/Low Ventilation mode Auto Humidifier switching (Only GUF-50/100RDH3) Possible (When heating) Operation mode switching Heat/Cool/Fan Filter maintenance indicator (Optional setting) 3,000 h/1,500 h/4,500 h/No display Error Display

• OA processing unit cannot be interlocked to another one.

• OA processing units set to group registration (non-interlocked) cannot be interlocked setting.

Restrictions and precautions

• When the OA processing unit is set to group registration, set the OA processing unit DIP switch 3-1 to on.

•

To connect two MA Remote controllers to the same group, set one MA Remote controller as a subremote controller.

•

MA Remote controllers and other local remote controllers cannot be used together in the same group.

OperationMonitoring

Scheduling/

Recording

Note: *1 When in the “Heating” mode, the humidifier will also operate.

*2 When the “Heating” is displayed on the controller, the humidifier is also operating. *3 “Dry” mode cannot be selected. *4 “Dry” display flashes. It indicates “Dry” mode is prohibited.

CHAPTER 3 ● Control System Design Section

1.3 System Design. Example 3

Central controller system with MELANS

Features

●

The Mitsubishi Electric air-conditioner network system (MELANS) can operate and monitor each group of OA processing units and air-conditioners.

●

Can also perform operations using OA processing unit remote controller.

System example

The following groups can be configured.

Group 1 : Group of multiple indoor units and one OA processing unit in interlocked operation. Group 2 : Group of one indoor unit with two remote controllers and one OA processing unit in interlocked operation. Group 3, 4 : Group of multiple groups and one OA processing unit in interlocked operation. Group 5 : Group of multiple OA processing units.

(

000

)

(

051

)

(

001

)

(

003

)

(

005

)(

007

)

(

002

) (

004

)

(

010

)

(

009

)

(

006

) (

008

)

Outdoor unit

Centralized controller

Power supply

unit

( ) address

Indoor unit

Indoor

unit

Indoor

unit

Indoor unit

Group 1

Group 5

Group 2 Group 3 Group 4

MA Remote controller

MA Remote

controller

MA Remote

controller

MA Remote

controller

MA Remote

controller

OA processing unit

OA processing

unit

OA processing

unit

OA processing

unit

Note:●On OA processing unit for a non-interlocked OA processing unit group, set DIP switch 3-1 (synchronous

air conditioning switch) to on. (In the system example shown above, Group 5 is non-interlocked OA processing unit.)

●

Perform group setting by specifying the same content as the group setting implemented for MA Remote controller wiring from the MELANS (centralized controller).

●

To operate OA processing units and indoor units by interlocking, it is necessary to perform interlock setting from the MELANS. (For a system that uses the MELANS, be sure to perform interlock setting from the MELANS, not from a local remote controller.)

Mitsubishi Y04-003 DATA BOOK

Specifications and Main Features

Frequently Asked Questions

User Manual

CONTENTS

CHAPTER 1

Product Section

1. Summary

2. Main Functions of OA Processing Unit

3. Model Line-Up

4. Summary of Types

5. Specifications

6. Outline Drawings

7. Electric Wiring Diagrams

8. Characteristic Curves

9. Construction and Principle of Heat Recovery Unit (Lossnay Core)

10. Total Heat Recovery Characteristics

11. Principle and Features of Permeable Film Humidifier

12. Cooling and Heating Characteristics

13. Filter Characteristics

14. Noise Characteristics

15. Reference Documents

CHAPTER 2

Air Conditioning System

Design Section

1. Guide to a Comfortable Air Conditioning System

2. Features of the OA Processing Unit

3. Air Conditioning and Ventilation

4. Characteristics

5. Lossnay Core Effect

6. Humidifying

7. Humidifying Effect of the OA Processing Unit

8. Water Quality and Service Life of Humidifier

9. Dust Removal

10. Sound

11. Precautions when Using

CHAPTER 3

Control System

Design Section

1. System Selection