Mitsubishi LGH-F300RX5-E, LGH-F470RX5-E, LGH-F600RX5-E, LGH-F1200RX5-E Technical Manual

June.2012

TECHNICAL MANUAL FOR NORTH AMERICA

Models Lossnay Unit

LGH-F300RX5-E
LGH-F470RX
LGH-F600RX
LGH-F1200RX

5-E

5-E

5-E

Lossnay Remote Controller

PZ-60DR-E
PZ-41SLB-E
PZ-52SF-E

Y11-001 Jun.2012 <MEE>

CONTENTS

Lossnay Unit

CHAPTER 1 Ventilation for Healthy Living

1. Necessity of Ventilation

2. Ventilation Standards

3. Ventilation Method

4. Ventilation Performance

5. Ventilation Load

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CHAPTER 2 Lossnay Construction and Technology

1. Construction and Features

2. Lossnay Core Construction and Technology

3. Total Energy Recovery Efficiency Calculation

4. What is a Psychrometric Chart?

5. Lossnay Energy Recovery Calculation

CHAPTER 3 General Technical Considerations

1. Lossnay Energy Recovery Effect

2. Calculating Lossnay Cost Savings

3. Psychrometric Chart

4. Determining Lossnay Core Resistance to Bacterial Cross-Contamination and Molds

5. Lossnay Core Fire : retardant property

6. Lossnay Core Sound Reducing Properties Test

7. Changes in the Lossnay Core

8. Comparing Energy Recovery Techniques

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U-2
U-3
U-4
U-7
U-9

U-16
U-16
U-18
U-19
U-20

U-22
U-24
U-26
U-28
U-30
U-31
U-32
U-34

CHAPTER 4 Characteristics

1. How to Read the Characteristic Curves

2. Calculating Static Pressure Loss

3. How to Obtain Efficiency from Characteristic Curves

4. Sound

5. NC Curves

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CHAPTER 5 System Design Recommendations

1. Lossnay Operating Environment

2. Sound Levels of Lossnay units with Built-in Fans

3. Attaching Air Filters

4. Constructing the Ductwork

5. Bypass Ventilation

6. Night purge function

7. Transmission Rate of Various Gases and Maximum Workplace Concentration Levels

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

9. Automatic Ventilation Switching

10. Alternate Installation for Lossnay

11. Installing Supplementary Fan Devices

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U-38
U-38
U-41
U-42
U-48

U-52
U-53
U-53
U-53
U-53
U-53
U-53
U-54
U-55
U-56
U-57

i

CHAPTER 6 Examples of Lossnay Applications

1. Large Office Building

2. Small-Scale Urban Building

3. Hospitals

4. Schools

5. Convention Halls, Wedding Halls in Hotels

6.

Public Halls (Facilities such as Day-care Centers)

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CHAPTER 7 Installation Considerations

1. LGH-Series Lossnay Ceiling Embedded-Type (LGH-RX5 Series)

CHAPTER 8 Filters

1. Importance of Filters

2. Dust

3. Calculation Table for Dust Collection Efficiency for Each Lossnay Filter

4. Comparing Dust Collection Efficiency Measurement Methods

5. Calculating Dust Concentration Levels

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CHAPTER 9 Service Life and Maintenance

1. Service Life

2. Cleaning the Lossnay Core and Pre-lter

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CHAPTER 10 Ventilation Standards in Each Country

1. Ventilation Standards in Each Country

2. United States of America
3 . United Kingdom

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U-60
U-64
U-65
U-67
U-68
U-69

U-72

U-76
U-76
U-77
U-78
U-80

U-82
U-82

U-86
U-87
U-87

CHAPTER 11 Lossnay Q and A

Note: The word “LGH-F300 to 1200RX5-E” in this Lossnay Technical Manual expresses both the products for 50Hz area and

60Hz area, except for some parts where model name difference are written clearly.

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U-90

ii

Lossnay Remote Controller

1. Summary

2. Applicable Models

3. Terminology

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4. System Features and Examples

4.1 Features

4.2 System Examples

4.3 System Selection

4.4 Basic System

4.5 Interlocking with M-Series or P-Series

4.6 Combining with City Multi

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5. Examples of Applications Using Various Input and Output Terminals

5.1 External Control Operating Mode Selection

5.2 Delayed Interlocked Operation

5.3 Multiple External Device Operation (PZ-60DR-E, PZ-41SLB-E, M-NET)

5.4 Multiple Lossnay Units Interlocked with One Indoor Unit (M-NET only)

5.5 Operation monitor output

5.6 Malfunction monitor output

5.7 By-pass operation monitor output

5.8 Connection Method

5.9

When switching High/Low/Extra-Low fan speed externally (when CO2 sensor or other equipment is connected)

5.10 When switching By-pass externally

5.11 When using the remote/local switching and the ON/OFF input (level signal)

5.12

When connecting to the City Multi, Lossnay remote controller (PZ-52SF-E) or Mitsubishi Electric Air-Conditioner Network System (MELANS)

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C-3

C-3

C-4

C-5
C-6
C-8
C-11
C-13
C-14

C-23
C-24
C-24
C-25
C-26
C-26
C-26
C-26
C-28
C-29
C-29
C-30

6. Precautions When Designing M-NET Systems

6.1 M-NET Transmission Cable Power Supply

6.2

Restrictions When the Lossnay Units are Connected to the Central Controller M-NET Transmission Cable

6.3 Wiring Example

6.4 Power Supply to the Indoor Unit Transmission Cable

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7. M-NET Cable Installation

7.1 Precautions When Installing Wiring

7.2 Electrical Wiring

7.3 Control Cable Length

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8. M-NET System Designs

8.1 Address Denitions

8.2 Precautions When Setting the Groups (when not interlocked with City Multi indoor units)

8.3 Precautions When Performing Interlock Settings (when interlocked with City Multi indoor units)

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C-31
C-31
C-32
C-33

C-34
C-35
C-36

C-37
C-39
C-39

iii

9. Automatic Ventilation Switching

9.1 Effect of Automatic Ventilation Mode

9.2 Ventilation mode control

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10. Troubleshooting

10.1 Service Flow

10.2 Checklist

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11. Installation method

11.1 Electrical installation

11.2 Connecting the power supply cable

11.3 System conguration

11.4 Function Setting

11.5 Trial operation

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12. Lossnay Remote Controller (PZ-60DR-E)

12.1 Parts Names

12.2 Setting the Day of the Week and Time

12.3 Using the Remote Controller

12.4 Care and Maintenance

12.5 Servicing

12.6 How to Install

12.7 Test Run

12.8 Function Selection

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C-40
C-40

C-44
C-45

C-64
C-66
C-66
C-72
C-76

C-78
C-79
C-79
C-83
C-83
C-84
C-85
C-86

13. Lossnay Remote Controller (PZ-41SLB-E)

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14. Lossnay M-NET Remote Controller (PZ-52SF-E)

15. Appendix

15.1 Centralized Controller (AG-150A)

15.2 Remote Controllers for M-Series or P-Series indoor units

15.3 ME Remote Controller (PAR-F27MEA)

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C-91

C-92

C-93
C-100
C-103

iV

Lossnay Unit

CHAPTER 1

Ventilation for Healthy Living

CHAPTER 1 • Ventilation for Healthy Living

Ventilation air must be introduced constantly at a set ratio in an air-conditioning system. The ventilation air introduced is to be
mixed with the return air to adjust the temperature and humidity, supply oxygen, reduce odors, remove tobacco smoke, and to
increase the air cleanliness.
The standard ventilation (outdoor air intake) volume is determined according to the type of application, estimated number of
occupants in the room, room area, and relevant regulations. Systems that accurately facilitate these requirements are required
in buildings.

1. Necessity of Ventilation

The purpose of ventilation is basically divided into “oxygen supply”, “air cleanliness”, “temperature control” and “humidity control”.
Air cleanliness includes eliminating “odors”, “gases”, “dust” and “bacteria”. Ventilation needs are divided into “personal comfort”,
“optimum environment for animals and plants”, and “optimum environment for machinery and constructed materials”.
Ventilation regulations are detailed in a variety of codes and standards applied to mechanical systems in buildings. Energy
efficiency codes also often apply to the design of ventilation systems.

1.1 Room Air Environment in Buildings

In Japan, the “Building Management Law”, a law concerning the sanitary environment in buildings, designates 11 applications
including offices, shops, and schools with a total floor area of 32,300ft2 (3,000m2) or more, as buildings. Law maintenance
and ventilation, water supply, discharge management according to the Environmental Sanitation Management Standards is
obligatory.

The following table gives a specific account of buildings in Tokyo.
(Tokyo Food and Environment Guidance Center Report)

Specic Account of Buildings in Tokyo (March, 2003)

Number of Buildings %

Offices 1,467 56.7

Shops 309 22.0

Department Stores 63 2.4

Schools 418 16.2

Inns 123 4.8

Theaters 86 3.3

Libraries 12 0.5

Museums 11 0.4

Assembly Halls 63 2.4

Art Museums 8 0.3

Amusement Centers 27 1. 0

Total 2,587 100.0

Note: Excludes buildings with an expanded oor space of 32,300 to 58,820ft2 (3,000 to 5,000m2) in particular areas.

Results of the air quality measurement public

Percentage Unsuitable Air Quality by Year

inspection and the standard values that were
not met (percentage of unsuitability) for the
approximately 500 buildings examined in 1980
are shown in the chart at the right.

There was a large decrease in high percentages

60

50

40

relative humidity

carbon dioxide

temperature

carbon monoxide

ventilation

floating particles
(tobacco smoke)

of floating particles, but there was almost no
change in temperature and carbon dioxide. The

30

highest percentage of unsuitability in 2006 is
relative humidity with 36%, followed by carbon
dioxide at 28%.

20

10

Percentage of unsuitable air quality (%)

0

76 77 7879 80 8171 73 75

(From reference data in the 2006 edition of the “Water Supply
Division, Dept. of Localized Public Health, Tokyo Metropolitan
Government, Bureau of Public Health”)

82

83 84

87

85

88 899091 92 93 94 95 96 97 98 9900 01 02 03 0405 06

86

(year)

U-2

CHAPTER 1 • Ventilation for Healthy Living

In Japan, an Instruction Guideline based on these regulations has been issued, and unified guidance is followed. Part of the
Instruction Guideline regarding ventilation is shown below.

The ventilation air intake must be 33ft (10m) or higher from ground level, and be located at an appropriate distance from the

•

exhaust air outlet. (Neighbouring buildings must also be considered.)

The ventilation air intake volume must be 15 to 18 CFM·occupant. (25 to 30 m3/h·occupant.)

•

An air volume measurement access hole must be installed at an appropriate position to measure the treated air volume of

•

the ventilating device.

Select the position and shape of the supply diffuser and return grille to evenly distribute the ventilation air in the room.

•

1.2 Effect of Air Contamination

Effect of Oxygen (O2) Concentration

Concentration (%) Standards and Effect of Concentration Changes

Approx. 21 Standard atmosphere.

20.5

20 - 19

18 Industrial Safety and Health Act. (Hypoxia prevention regulations.)

16 Normal concentration in exhaled air.

16 - 12

15 Flame in combustion devices will extinguish.

12 Short term threat to life.

7 Fatal

Ventilation air volume standard is a guideline where concentration does not decrease more than 0.5%
from normal value. (The Building Standard Law of Japan)

Oxygen deciency 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.

Increase in pulse and breathing; resulting in dizziness and headaches.

Effect of Carbon Monoxide (CO) 10,000 ppm = 1%

Concentration (ppm)

0.01 - 0.2 Standard atmosphere.

5 Tolerable long-term value.

10

20

50

100

200 Light headache in the frontal lobe in 2 to 3 hours.

400 Headache in the temporal lobe, 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 %)

The Building Standard Law of Japan, Law for Maintenance of Sanitation in Buildings.
Environmental standard for a 24-hour average.

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

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

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

Level may be found in automobile exhaust.

Effect of Concentration Changes

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

U-3

CHAPTER 1 • Ventilation for Healthy Living

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 occupants stay in the space for long time.

0.10

0.15 Tolerable concentration used for ventilation calculations.

0.2 - 0.5 Relatively poor.

0.5 or more Very poor.

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

2 Depth of breathing and inhalation volume increases 30%.

3 Work and physical functions deteriorate, increase breathing doubles.

4 Normal exhalation concentration.

4 - 5

8

18 or more Fatal

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

General tolerable concentration.
The “Building Standard Law” of Japan, “Law for Maintenance of Sanitation in Buildings”.

The respiratory center is stimulated; depth and times of breathing increases. Dangerous if inhaled for a
long period. If an O2 deciency also occurs, conditions will rapidly deteriorate and become dangerous.

When inhaled for 10 minutes, breathing difficulties, redness in the face and headaches will occur.
Conditions will worsen when there is also an O2 deciency .

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.

1.3 Effect of Air Contamination in Buildings

Dirtiness of interior

•

New ceilings, walls and ornaments will turn yellow from dust in 1 to 2 years.

2. Ventilation Standards

The legal standards for ventilation differ according to each country. Please follow the standards set by your country. In the U.S.,
ASHRAE revised their standards in 1989 to become more strict.

U-4

CHAPTER 1 • Ventilation for Healthy Living

3. Ventilation Method

3.1 Comparing of Ventilation Methods

There are two main types of ventilation methods.

Centralized Ventilation Method

Mainly used in large buildings, with the ventilation air intake being installed in one machine room. For this method, primary
treatment of the ventilation air, such as energy recovery to the intake air and dust removal, is performed via distribution to the
building by ducts.

Independent Zoned Ventilation Method

Mainly used in small to medium sized buildings, with areas being ventilated using ventilation air intake via independent
ventilation devices. The use of this method has recently increased as independent control is becoming more feasible.

Centralized Ventilation Method Independent Zoned Ventilation Method

1) System operation with cassette-type indoor units of air conditioner

Air intake

(ventilation

air)

Filters

Lossnay

Exhaust

Supply fan

Each unit

Air exhaust
(stale air)

Cassette-type indoor units of
air conditioner or fan coil unit

Exhaust grill

Ceiling recessed­type Lossnay

Finished ceiling

Exhaust air
Ventilation air

2) System operation with ceiling embedded-type indoor units of air conditioner

Ceiling embedded-type indoor units
of air conditioner or fan coil unit

3)

Independent operation with ceiling suspended-type indoor units of air conditioner

Cassette-type or ceiling
suspended-type indoor units of
air conditioner or fan coil unit

Exhaust grill

Supply grill

Ceiling recessed­type Lossnay

Finished ceiling

Exhaust grill

Finished ceiling

Exhaust air
Ventilation air

Ceiling recessed­type Lossnay

Exhaust air
Ventilation air

U-5

CHAPTER 1 • Ventilation for Healthy Living

Comparing Centralized Ventilation and Independent Zoned Ventilation Methods

Centralized Ventilation Method Independent Zoned Ventilation Method

Fan Power

Installation Area

Zoning

System Flexibility

Design

Control

The air transfer distance is long, thus requiring
much fan power.

• Independentequipmentroomisrequired.

• Ductspaceisrequired.

• Penetrationofoorswithverticalshaftisnot

recommended in terms of re prevention.

Generalized per system. Can be used for any one area.

• Designofouterwallisnotlost.

• Theindoorsupplyairdiffuserandreturngrillecan

be selected without restrictions for an appropriate
design.

• Astheusagesettimeandventilationvolume

control, etc., are 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 occupants.

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.

• Thenumberofintakesandexhaustairoutletson

an outside wall will increase; design must be
considered.

• Thedesignwillbexedduetoinstallationttings,

so the design of the intakes and exhaust air
outlets must be considered.

• Theuserineachzonecanoperatetheventilator

without restrictions.

• Theventilatorcanbeoperatedevenduringoff-

peak hours.

Comfort

Maintenance and
Management

Trouble inuence

System Management

Costs

• Anidealsupplyairdiffuserandreturngrille

position can be selected as the supply air diffuser
and return grille can be positioned without
restrictions.

•

The only noise in the room is the sound of air movement.

• Antivibration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.

• Theentiresystemisaffected.

• Immediateinspectioncanbeperformedinthe

equipment room.

Because there are many common-use areas, if the
building is a tenant building, an accurate
assessment of operating cost is difficult.

• Considerationmustbemadebecauseofthe

noise from the main unit.

• Antivibrationmeasuresareoftennotrequiredas

the unit is compact and any generated vibration
can be dispersed.

• Workefficiencyispoorbecause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.

Invoicing for each zone separately is possible, even
in a tenant building.

U-6

CHAPTER 1 • Ventilation for Healthy Living

4. Ventilation Performance

The ventilation performance is largely affected by the installation conditions. Optimum 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 “wind pressure (static pressure)”.

4.1 Air Volume

Air volume equals the volume of air exhausted (or supplied) by the unit in a given period, and is expressed in CFM or m3/hr (hour).

4.2 Wind Pressure

When a piece of paper is placed in front of a fan then released, the piece of paper will be blown away. The force that blows the
paper away is called wind pressure and is normally expressed in inH2O. Wind pressure is divided into the following three types:

4.2.1 Static Pressure

The force that effects the surroundings when the air is contained such as in an automobile tyre or rubber balloon. For example,
in a water gun, the hydraulic pressure increases when pressed by a piston. If there is a small hole, the water is forced out of
that opening. The pressure of the water is equivalent to air static pressure. The higher the pressure, the farther the water (air)
can be forced out.

4.2.2 Dynamic Pressure

The speed at which air flows; for example, the force at which a hurricane presses against a building.

4.2.3 Total Pressure

The total force that wind has, and is the sum of the static pressure and dynamic pressure.

U-7

CHAPTER 1 • Ventilation for Healthy Living

4.3 Measuring the Air Volume and Static Pressure

Mitsubishi Electric measures the Lossnay’s air volume and static pressure with a device as shown below according to Japan
Industrial Standards (JIS B 8628).

Measuring Device Using Orice (JIS B 8628 Standards)

Chamber

Damper

Smoothing
net

Wind gauge

duct path

Orice

Connection

Supply

Air

(SA)

Test unit

Blower

Pressure

difference before

and after orice

(Air volume

measurement)

Static pressure in chamber
(Static pressure measurement)

A) When measuring the supply air volume (with the orice plate)

Wind gauge

duct path

Smoothing

grid

Orice

Wind dispersing place

Smoothing

Return

Air

(RA)

net

B) When measuring the return air volume (with the orice plate)

Smoothing

grid

Blower

Connection

Test unit

Static pressure in chamber
(Static pressure measurement)

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 (Point A, 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 median 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).

U-8

)

Static pressure (

H

Air volume (Q)

CHAPTER 1 • Ventilation for Healthy Living

5. Outdoor Air (ventilation) Load

5.1 How to Calculate Each Approximate Load

5.1 A (US unit)

The ventilation air load can be calculated with the following formula if the required ventilation intake volume “Q CFM” is known:

(Ventilation air load) = γ · QF · (iO - iR)

=

γ [lb/ft3] × S[ft2] × k × n [occupant/ft2] × Vf [CFM / occupant] × (iO - iR): ∆i [Btu/lb]

: Specific air gravity - 0.0749 lb/ft

γ

S : Building’s airconditioned area
k : Thermal coefficient; generally 0.7 - 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 : Ventilation air intake volume per occupant
Refer to the Required ventilation air intake volume per occupant table below.
iO : Ventilation air enthalpy - Btu/lb
iR : Indoor enthalpy - Btu/lb

Floor Space per Occupant (ft2)
(According to the Japan Federation of Architects and Building Engineers Associations)

3

Office Building

General Design 43 - 75 5.4 - 21.5 5.4 - 21.5 54 - 86 10.8 - 21.5 4.3 - 6.5

Value 54 32.3 10.8 64.6 16.1 5.4

Average Crowded Empty

Department Store, Shop

Restaurant

Theater or

Cinema Hall

Required Ventilation Air Intake Volume Per Occupant (CFM per occupant)

Required Ventilation Volume

50 30

30 25

15

15 10

15
20

10
12

10
15

Amount of Cigarette Smoking

Extremely Heavy

Quite Heavy

Heavy

Light

None

Application Example

Broker’s office
Newspaper editing room
Conference room

Bar
Cabaret

Office
Restaurant

Shop
Department store

Theater
Hospital room

Recommended Value Minimum Value

Caution

The amount of smoking that could be present in each type of room must be carefully considered when obtaining the

required ventilation volume shown in the table above.

U-9

CHAPTER 1 • Ventilation for Healthy Living

5.1 B (SI unit)

The ventilation air load can be calculated with the following formula if the required ventilation intake volume “Q m3/h” is known:

(Ventilation air load) = γ · QF · (iO - iR)

=

[kg/m3] × S [m2] × k × n [occupant/m2] × Vf [m3/h·occupants] × (iO - iR): ∆i [kJ/kg]

γ

: Specific air gravity - 1.2 kg/m

γ

S : Building’s air-conditioned area
k : Thermal coefficient; generally 0.7 - 0.8.
n :

The average population concentration is the inverse of the occupancy area per occupant. If the number of occupants in the

room is unclear, refer to the Floor space per
Vf : Ventilation air intake volume per
Refer to the Required ventilation air intake volume per
iO : Ventilation air enthalpy - kJ/kg
iR : Indoor enthalpy - kJ/kg

Floor Space per Occupant (m2)
(According to the Japan Federation of Architects and Building Engineers Associations)

3

occupant

occupant

table below.

occupant

table below.

Office Building

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

Value 5 3.0 1. 0 6.0 1. 5 0.5

Average Crowded Empty

Department Store, Shop

Restaurant

Theater or

Cinema Hall

Required Ventilation Air Intake Volume Per Occupant (m3/h·occupant)

Required Ventilation Volume

85 51

51 42.5

25.5

25.5 17

25.5
34

17

20

17

25.5

Amount of Cigarette Smoking

Extremely Heavy

Quite Heavy

Heavy

Light

None

Application Example

Broker’s office
Newspaper editing room
Conference room

Bar
Cabaret

Office
Restaurant

Shop
Department store

Theater
Hospital room

Recommended Value Minimum Value

Caution

The amount of smoking that could be present in each type of room must be carefully considered when obtaining the
required ventilation volume shown in the table above.

U-10

CHAPTER 1 • Ventilation for Healthy Living

See below for Calculation examples of determining ventilation load during both cooling and heating.

5.2 Ventilation Load During Cooling (In an Office Building)

Cooling Load Classications

•

(a) Indoor penetration heat

(b) Indoor generated heat

(c) Reheating load (qRL)

(d) Outdoor air load

(a) Is the heat penetrating the room, and often is 30 to 40% of the entire cooling load?
(b) Is the heat generated in the room?
(c) Is applies only when reheating is necessary?
(d) Is the heat generated when ventilation air is mixed into part of the supply air diffuser volume and introduced into the room?
The ventilation air is introduced to provide ventilation for the room occupants, and is referred to as the ventilating load.

Office Building

Department Store, Shop

Heat generated from walls (qWS)

Heat generated from glass

Accumulated heat load in walls (qSS)

Generated heat from occupants

Generated heat from electrical equipment

Sensible heat (qFS)
Latent heat (qFL)

from direct sunlight (qGS)
from conduction and convection (qGS)

Sensible heat (qHS)
Latent heat (qHL)

Sensible heat (qES)
Latent heat (qEL)

Typical Load Values During Cooling

Load Type Load

4.9 W/ft2 (53.0 W/m2)

Occupants 2.5 W/ft2 (26.4 W/m2)

Lighting Equipment 2.8 W/ft2 (30.0 W/m2)

Total 14.6 W/ft2 (157.0 W/m2)

Ventilation air
load 33.8%

4.9 W/ft
(53.0 W/m2)

2

Indoor

generated heat

(occupants, lighting

equipment) 35.9%

5.2 W/ft2 (56.4 W/m2)

Indoor
penetration
heat 30.3%

2

4.4 W/ft
(47.6 W/m2)

2

14.6 W/ft

(157.0 W/m2 )

Ventilation Air Load

Indoor
Generated Heat

Indoor Penetration Heat 4.4 W/ft2 (47.6 W/m2)

Conditions: Middle south-facing oor of a typical office building.

Cooling Load Per Unit Area

When the volume of ventilation air per occupants is 15 CFM (25 m3/h), and the number of occupants per 1 ft2 is 0.0186 (1 m2 is

0.2), the cooling load will be approximately 14.6 W/ft2 (157.0 W/m2).

Ventilation Load

•

Standard design air conditions in Tokyo

Cooling

Dry Bulb Temp.

Outdoor Air 91.4°F (33 °C) 63% 80.6°F (27 °C) 36.5 Btu/Ib (85 kJ/kg)

Indoor Air 78.8°F (26 °C) 50%

Relative Humidity

Wet Bulb Temp. Enthalpy Enthalpy Difference

65.7°F (18.7 °C)

22.9 Btu/Ib (53.2 kJ/kg)

13.6 Btu/Ib (31.8 kJ/kg)

<US unit>
When the load per floor area of 1 ft2 with a ventilation volume of 15 CFM·occupant is calculated with the air conditions detailed
above, the following is obtained:
Ventilation air load = 0.0749 Ib/ft3 (Specific gravity of air) × 0.0186 occupant/ft2 (number of occupants per 1 ft2)
× 15 CFM·occupants (ventilation air volume) × 13.7 Btu/Ib (air enthalpy difference indoor/outdoor) = 0.286 Btu/min·ft2 (4.9 W/ft2)

<SI unit>
When the load per floor area of 1 m2 with a ventilation volume of 25 m3/h·occupant is calculated with the air conditions detailed
above, the following is obtained:
Ventilation air load = 1.2 kg/m3 (Specific gravity of air) × 0.2 occupant/m2 (number of occupants per 1 m2)
× 25 m3/h·occupants (ventilation air volume) × 31.8 kJ/kg (air enthalpy difference indoor/outdoor) = 190.8 kJ/h·m2 (53.0 W/m2)

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

U-11

CHAPTER 1 • Ventilation for Healthy Living

Determining Internal Heat Gain

•

When classifying loads, the internal heat gain (indoor generated heat + indoor penetration heat) is the ventilation air load
subtracted from the approximate cooling load when it is assumed that there is no reheating load.

(Internal heat gain)

= 14.6 W/ft2 (157.0 W/m2) – 4.9 W/ft2 (53.0 W/m2) = 9.7 W/ft2 (104.0 W/m2)

The value of internal heat gain is based on assumptions for typical loads. To determine individual levels of internal heat gain,

•

the following is suggested:

Indoor Generated Heat

•

(1) Heat generated from occupants

Heat generation design value per person (occupant) in the office:

Sensible heat (SH) = 63.0 W/person (W·occupant)
Latent heat (LH) = 69.0 W/person (W·occupant)
Total heat (TH) = 132.0 W/person (W·occupant)

The heat generated per 1 ft2 (m2) of oor space:

Heat generated from occupants = 132.0 W/person (132.0 W·occupant) × 0.0186 person/ft2 (0.2 occupant/m2) = 2.5W/ft2 (26.4 W/m2)

(2) Heat generated from electrical equipment (lighting)

The approximate value of the lighting and power required for a general office with lighting of 300 - 350 Lux, is 1.9 - 2.8 W/ft2
(20 - 30 W/m2).

Heat generated from electrical equipment (lighting) = 30 W/m

Indoor Penetration Heat

•

The heat that penetrates into the building from outside, which can be determined by subtracting the amount of heat generated
by occupants and lighting from the internal heat gain.

(Indoor infiltration heat)

= 9.7 - (2.5 + 2.8) = 4.4 W/ft2 (104.0 – (26.4 + 30.0) = 47.6 W/m2)

2

U-12

CHAPTER 1 • Ventilation for Healthy Living

5.3 Ventilation Load During Heating

Classication of Heating Load

•

Class Heat Load

Heat escaping from walls (qWS)

(a)

(b)

During heating, the heat generated by occupants and electrical equipment in the room can be subtracted from the heating load.
If the warming-up time at the start of heating is short, however, the generated heat may be ignored in some cases.

Percentage of Load

air load 41.9%

Indoor heat

loss

Ventilation

load

Ventilation

5.2 W/ft2

(56.0 W/m2)

Indoor heat
loss 58.1%

7.2 W/ft

(77.7 W/m2)

Heat escaping from glass (qGS)

Heat loss from conduction and convection (qGS)

Accumulated heat load in walls (qSS)

Sensible heat (qFS)

Latent heat (qFL)

Ventilation Air Load

Internal Heat 7.2 W/ft2 (77.7 W/m2)

2

Conditions: Middle south-facing oor of a typical office building.

Type of Load Load

5.2 W/ft2 (56.0 W/m2)

Total 12.4 W/ft2 (133.7 W/m2)

12.4 W/ft2
(133.7 W/m2)

Heating Load Per Unit Area

•

When the ventilation air volume per occupant is 15 CFM (25 m3/h), and the number of occupants per 1 ft2 is 0.0186 (1 m2
is 0.2), the heating load will be approximately 12.4 W/ft2 (133.7 W/m2).

Internal Heat Loss

•

In terms of load classification, the internal heat loss is the value of the ventilation air load subtracted from the approximate
heating load.
Internal heat loss = 12.4 W/ft2 – 5.2 W/ft2 = 7.2 W/ft2 (133.7 W/m2 – 56.0 W/m2 = 77.7 W/m2)

Ventilation Load

•

Standard design air conditions in Tokyo

Dry Bulb Temp.

Heating

<US unit>
When the load per 1 ft2 of floor area with a ventilation volume of 15 CFM·occupant is calculated with the air conditions
detailed above, the following is obtained:
Ventilation air load = 0.749 Ib/ft3 × 0.0186 occupants/ft2 × 15 CFM·occupant × 14.4 Btu/Ib = 0.30 Btu/min·ft2 (5.2 W/ft2)

<SI unit>
When the load per 1 m2 of floor area with a ventilation volume of 25 m3/h·occupant is calculated with the air conditions
detailed above, the following is obtained:
Ventilation air load = 1.2 kg/m3 × 0.2 occupants/m2 × 25 m3/h·occupant × 33.5 kJ/kg = 201.0 kJ/h·m2 (56 W/m2)

Outdoor Air 32 °F (0 °C) 50% 26.6 °F (–3 °C) 2.1 Btu/Ib (5.0 kJ/kg)

Indoor Air 68 °F (20 °C) 50%

Relative Humidity

Wet Bulb Temp. Enthalpy Enthalpy Difference

56.7 °F (13.7 °C)

16.6 Btu/Ib (38.5 kJ/kg)

14.4 Btu/Ib (33.5 kJ/kg)

The Lossnay recuperates approximately 70% of the ventilation load and saves on approximately 30% of the total load.

U-13

CHAPTER 2

Lossnay Construction and Technology

CHAPTER 2 • Lossnay Construction and Technology

1. Construction and Features

Construction

•

Lossnay is constructed so that the exhaust air passage from the
indoor side to the outdoor side (RA → EA) and the ventilation air
passage from the outdoor side to the indoor side (OA → SA) cross.
The Lossnay Core is located at this crosspoint, and recovers the
heat by conduction through the separating medium between these
airflows. This enables the heat loss during exhaust to be greatly
reduced.

* RA : Return Air
EA : Exhaust Air
OA : Outdoor Air
SA : Supply Air

Main Features

(1) Cooling and heating maintenance fees are reduced while ventilating.

(2) The system size of Heating/cooling system and cooling/heating load can be reduced.

(3) Dehumidifying during summer and humidifying during winter is possible.

(4) Comfortable ventilation is possible with the outdoor air can be adjusted to parallel the room temperature.

(5) Sound can be reduced.

SA (Supply air diffuser)

Supply fan

RA (Return air)

Exhaust side lter

Note: The duct inlet and outlet are linear in the

actual product.

Lossnay Core

EA (Exhaust air)

Exhaust fan

OA (Outdoor air)

Intake side lter

2. Lossnay Core Construction and Technology

Simple Construction

•

The Lossnay core is a cross-air passage total energy recovery unit
constructed from specially treated membrane with a corrugated
structure.
The fresh air and exhaust air passages are totally 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 membrane. Total heat (sensible heat
plus latent heat) is transferred from the stale exhaust air to the
ventilation air being introduced into the system when they pass
through the Lossnay.

Treated membrane

•

The cellulose membrane partition plates are treated with special
chemicals so that the Lossnay Core is an appropriate energy
recovery unit for the ventilator.

The membrane has many unique properties:
(1) Incombustible and strong.

(2) Has selective hydroscopicity and moisture permeability that permits the passage of only water vapor (including some

water-soluble gases).

(3) Has gas barrier properties that does not permit gases such as CO

space.

SA
Supply Air
(Fresh heating/cooling air)

Partition
plate
(Treated
membrane)

Spacer plate
(Treated
membrane)

RA
Return Air
(Dirty heating/cooling air)

2 and other pollutants from entering the conditioned

Indoors Outdoors

EA
Exhaust Air
(Stale air)

OA
Outdoor air
(Fresh air)

U-16

CHAPTER 2 • Lossnay Construction and Technology

Total Energy Recovery Mechanism

•

Sensible Heat and Latent Heat

The heat that enters and leaves in accordance with rising or falling temperatures is called sensible heat. The direct movement of
water vapor molecules or due to the changes in the matter’s physical properties (evaporation, condensation) is called latent heat.

(1) Temperature (Sensible Heat) Recovery

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

2) As shown in the diagram at right, the energy recovery
efficiency is affected by the resistance of the partition plate.
For Lossnay, there is little difference when compared to
materials such as copper or aluminium that also have high
thermal conductivity.

t1

Ra1

Rp

Ra2

t2

Heat Resistance Coefficients

Lossnay Plate 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) Recovery

Water vapor travels through the partition plate from the high

•

humidity to low humidity side via the differential pressure in
the vapor.

High humidity side

Partition plate
Ra1+Ra2»Rp

Low humidity side

Partition plate

U-17

CHAPTER 2 • Lossnay Construction and Technology

3. Total Energy Recovery Efficiency Calculation

The Lossnay Core’s energy recovery efficiency can be considered
using the following three transfer rates:

(1) Temperature (sensible heat) recovery efficiency

(2) Humidity (latent heat) recovery efficiency

(3) Enthalpy (total heat) recovery efficiency

The energy recovery effect can be calculated if two of the above
efficiencies are known.

Each energy efficiency can be calculated with the formulas in the

•

table.

When the supply and exhaust air volumes are equal, the energy

•

recovery efficiencies on the supply and exhaust sides are the
same.

When the supply and exhaust air volumes are not equal, the total

•

energy recovery efficiency is low if the exhaust volume is lower,
and high if the exhaust volume is higher.

Item Formula

Temperature recovery

efficiency (%)

Enthalpy recovery

efficiency (%)

ηt =

ηi =

tOA - tSA

tOA - tRA

iOA - iSA

iOA - iRA

×100

× 100

SA
Fresh air exhaust
(Fresh heating/cooling air)

RA
Stale air induction
(Dirty heating/cooling air)

η : Efficiency (%)

t : Dry bulb temperature (°F, °C)

i : Enthalpy (Btu/Ib, kJ/kg)

Indoors Outdoors

EA
Exhaust air
(Stale air)

OA
Fresh air
induction
(Fresh air)

Calculation of Supply Air Condition After Passing Through Lossnay

If the Lossnay energy recovery 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 in the following table.

Supply Side Exhaust Side

Temperature tSA = tOA - (tOA - tRA) × ηt tEA = tRA + (tOA - tRA) × ηt

Enthalpy iSA = iOA - (iOA - iRA) × ηi iEA = iRA + (iOA - iRA) × ηi

U-18

CHAPTER 2 • Lossnay Construction and Technology

4. What is a Psychrometric Chart?

A chart that 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
(total heat) of a certain air condition. If two of these values are known, the other values can be found with the chart. Now air
conditions will change when it is heated, cooled, humidified or dehumidified can also be seen easily on the chart.

(1) Dry Bulb Temperature t (°F, °C)

Generally referred to as standard temperature, the DB
temperature is obtained by using a dry bulb thermometer
(conventional thermometer).

Temperature (°F,°C)

(2) Wet Bulb Temperature t’ (°F, °C)

When a dry bulb thermometer is wrapped in a piece of wet
gauze and an ample air ow (3 m/s or more) is applied, the
heat from the air and evaporating water vapor applied to the
wet bulb will balance at an equal state and the wet bulb
temperature is obtained.

Wet bulb temperature

(dew point) t’ (°F, °C)

(3) Absolute Humidity x (Ib/Ib’, kg/kg’)

Weight (Ib, kg) of the water vapor that corresponds to the
weight (Ib’, kg’) of the dry air in the humid air.

(4) Relative Humidity ϕ (%)

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. Relative humidity is obtained with the following
formula:

ϕR = PW/PWS × 100

(5) Dew Point t” (°F, °C)

Water content in the air will start to condense when air is
cooled and the dry bulb temperature at that condition is the
dew point.

(6) Enthalpy i (Btu/Ib, kJ/kg)

Physical matter has a set heat when it is at a certain
temperature and state. The retained heat is called the
enthalpy, with dry air at 32 °F (0 °C) being set at 0.

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”

Parallel to absolute
temperature scale line

t” °F, °C dew point

Absolute humidity x (Ib/Ib’, kg/kg’)

A

Enthalpy i (Btu/Ib, kJ/kg)

U-19

CHAPTER 2 • Lossnay Construction and Technology

5. Lossnay Energy Recovery Calculation

The following diagram shows the various air conditions when ventilation air is introduced through the Lossnay Core. If a
conventional sensible energy recovery unit is used alone and is assumed to have the same energy recovery efficiency as
Lossnay, the condition of the air supplied to the room is expressed by Point A in the figure. Point A shows that the air is very
humid in summer and very dry in winter.
The air supplied to the room with Lossnay 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.

iOA

AO

iSA

Enthalpy (Btu/Ib, kJ/kg)

iOA

Outdoor air

iRA

iSA

Ventilation load

Lossnay Core energy recovery

O

tOA tSA

condition in

winter

Enthalpy (Btu/Ib, kJ/kg)

Dry bulb temperature (°F, °C)

i

RA

S

A

Ventilation load

Lossnay Core energy recovery

R

Supply air condition of

the Lossnay

Room air condition in winter

tRA tRA

Room air

condition

S

R

in summer

t

SA tOA

Supply air condition of

the Lossnay

The quantity of heat recovered by using the Lossnay Core can be calculated with the formula below:

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

Where

<US unit>
γ = Specic weight of the air

under standard conditions 75 (Ib/ft3)
Q = Treated air volume (CFM)
t = Temperature (°F)
x = Absolute humidity (Ib/Ib’)
i = Enthalpy (Btu/Ib)
η = Energy recovery efficiency (%)

<SI unit>
γ = Specic weight of the 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 = Energy recovery efficiency (%)

Outdoor air condition

in summer

XOA

XSA

XRA

Absolute humidity

(Ib/Ib’, kg/kg’)

XRA

XSA

XOA

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

U-20

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

CHAPTER 3

General Technical Considerations