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

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Page 1

June.2012

TECHNICAL MANUAL FOR NORTH AMERICA

Models Lossnay Unit

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

5-E

Lossnay Remote Controller

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

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Y11-001 Jun.2012 <MEE>

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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

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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

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

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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-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

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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

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Page 8

Lossnay Unit

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Page 10

CHAPTER 1

Ventilation for Healthy Living

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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

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

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

Percentage of unsuitable air quality (%)

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”)

83 84

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

(year)

U-2

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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.

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.

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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

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.

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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

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

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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.

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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.

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Page 17

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 (

Air volume (Q)

Page 18

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

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)

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 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.

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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]

: Specific air gravity - 1.2 kg/m

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)

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

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

Page 20

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

(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)

Indoor

generated heat

(occupants, lighting

equipment) 35.9%

5.2 W/ft2 (56.4 W/m2)

Indoor penetration heat 30.3%

4.4 W/ft (47.6 W/m2)

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

Page 21

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)

U-12

Page 22

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)

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

Page 23

Page 24

CHAPTER 2

Lossnay Construction and Technology

Page 25

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

Page 26

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.

Ra1

Ra2

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

Page 27

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

Page 28

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’)

Enthalpy i (Btu/Ib, kJ/kg)

U-19

Page 29

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

iSA

Enthalpy (Btu/Ib, kJ/kg)

iOA

Outdoor air

iRA

iSA

Ventilation load

Lossnay Core energy recovery

tOA tSA

condition in

winter

Enthalpy (Btu/Ib, kJ/kg)

Dry bulb temperature (°F, °C)

Ventilation load

Lossnay Core energy recovery

Supply air condition of

the Lossnay

Room air condition in winter

tRA tRA

Room air

condition

in summer

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

Page 30

CHAPTER 3

General Technical Considerations

Page 31

CHAPTER 3 • General Technical Considerations

1. Lossnay Energy Recovery Effect

1.1 Comparing Ventilation Load of Various Ventilators

Examples of formulas that compare the energy recovered and ventilation load when ventilating with the Lossnay (total energy recovery unit), a sensible energy recovery ventilation unit (sensible HRV), and a conventional ventilator unit are shown below.

(1) Cooling During Summer

Conditions

Model LGH-F600RX5-E

•

(at 60Hz, high speed) (For summer)

Ventilation rate: 600 CFM

•

(specic gravity of air ρ = 0.0749 Ib/ft3)

Supply air

Lossnay

Unit

Dry bulb temperature (°F)

Absolute humidity (Ib/Ib’)

Relative humidity (%)

Enthalpy (Btu/Ib)

Total energy recovered (kW)

Ventilation load (kW)

Ventilation load ratio (%)

Dry bulb

Indoor Unit

Air Conditioner

temperature Absolute

humidity Relative

humidity

Enthalpy

Room air

82.7 82.7 91.4

0.0159 0.0203 0.0203

66.0 84 63

29.6 34.5 36.4

4.7 1.6 0

5.5 9.3 10.9

50 86 100

78.8°F

0.0105 Ib/Ib’

50%

22.7 Btu/Ib

Energy recovery efficiency table (%)

•

Lossnay

Sensible HRV

Unit

Temperature (Sensible Heat)

Enthalpy (Total Heat)

69 69 –

50 14* –

* Calculated volume under conditions below.

Sensible HRV

Unit

Conventional

Ventilator Unit

Unit

Dry bulb temperature Absolute humidity Relative humidity

Enthalpy

Conventional

Ventilator Unit

Exhaust air

Outdoor air

91.4°F

0.0203 Ib/Ib’

63%

36.4 Btu/Ib

Calculation Example Summer Conditions

Lossnay Unit

•

(Supply air diffuser temperature) tSA = 91.4°F – (91.4°F – 78.8°F) × 0.69 = 82.7°F (Supply air diffuser enthalpy) hSA = 36.4 – (36.4 – 22.7) × 0.50 = 29.6 Btu/Ib Heat recovered (36.4 – 29.6) × 0.0749 × 600 = 304.4 Btu/min = 5.4 kW Ventilation load (29.6 – 22.7) × 0.0749 × 600 = 310.1 Btu/min = 5.5 kW

Sensible HRV Unit

•

(Supply air diffuser temperature) tSA = 91.4°F – (91.4°F – 78.8°F) × 0.69 = 82.7°F (Supply air diffuser enthalpy) hSA = 34.5 Btu/Ib (from psychrometric chart) Heat recovered (36.4 – 34.5) × 0.0749 × 600 = 85.4 Btu/min = 1.5 kW Ventilation load (34.5 – 22.7) × 0.0749 × 600 = 530.3 Btu/min = 9.3 kW [Calculated enthalpy recovery efficiency 85.4 ÷ (85.4 + 530.3) × 100 = 14%]

Conventional Ventilator Unit

•

If a conventional ventilator unit is used, the energy recovered will be 0 as the supply air diffuser is equal to the outdoor air. The ventilation load is: (36.4 – 22.7) × 0.0749 × 600 = 620.2 Btu/min = 10.9 kW

U-22

36.4

Enthalpy

(Btu/Ib)

29.6

iSA

Ventilation load

22.7

iRA

Dry bulb temperature (°F)

iOA

Lossnay energy recovery

Room air condition in summer

tRA

78.8

tSA

82.7

Outdoor air condition

in summer

Supply air condition

of the Lossnay

tOA

91.4

0.0203

XSA

0.0159

XRA

0.0105

Absolute humidity (Ib/Ib’)

Page 32

(2) Heating During Winter

Conditions:

Model LGH-F600RX5-E

•

(at 60Hz, high speed) (For winter)

Ventilation rate: 600 CFM

•

(Specic gravity of air ρ = 0.0749 Ib/ft3)

Supply air

Dry bulb temperature (°F)

Absolute humidity (Ib/Ib’)

Relative humidity (%)

Enthalpy (Btu/Ib)

Total energy recovered (kW)

Ventilation load (kW)

Ventilation load ratio (%)

56.8 56.8 32

0.0047 0.0018 0.0018

48.5 18.5 50

11.1 7.9 2.0

7.1 4.6 0

4.3 6.8 11.5

36 60 100

Room air

Indoor Unit

Air Conditioner

Dry bulb temperature

Absolute humidity

Relative humidity

Enthalpy

68°F

0.0073 Ib/Ib’

50%

16.6 Btu/Ib

Lossnay

Unit

Sensible HRV

CHAPTER 3 • General Technical Considerations

Energy recovery efficiency table (%)

•

Lossnay

Unit

Temperature (Sensible Heat)

Enthalpy (Total Heat)

69 69

64 40*

* Calculated volume under conditions below .

Unit

Conventional

Ventilator Unit

Sensible HRV

Unit

Dry bulb temperature

Absolute humidity

Relative humidity

Enthalpy

Conventional

Ventilator Unit

–

Exhaust air

Outdoor air

32°F

0.0018 Ib/Ib’

50%

2.0 Btu/Ib

Calculation Example Winter Conditions

Lossnay Unit

•

(Supply air diffuser temperature) tSA = (68°F – 32°F) × 0.69 + 32°F = 56.8°F (Supply air diffuser enthalpy) hSA = (16.6 – 2.0) × 0.64 + 2.0 = 11.3 Btu/Ib Heat recovered (11.3 – 2.0) × 0.0749 × 600 = 417.9 Btu/min = 7.3 kW Ventilation load (16.6 – 11.3) × 0.0749 × 600 = 238.2 Btu/min = 4.2 kW

Sensible HRV Unit

•

(Supply air diffuser temperature) tSA

= (68°F – 32°F) × 0.69 + 32°F = 56.8°F (Supply air diffuser enthalpy) hSA = 7.9 Btu/Ib (from psychrometric chart) Heat recovered (7.9 – 2.0) × 0.0749 × 600

= 265.1 Btu/min = 4.7 kW

Enthalpy

2.0

iOA

11.3

iSA

(Btu/Ib)

16.6

iRA

Ventilation load

Lossnay

energy recovery

Ventilation load (16.6 – 7.9) × 0.0749 × 600

= 391.0 Btu/min = 6.9 kW [Calculated enthalpy recovery efficiency 265.1 ÷ (265.1 + 391.0) × 100 = 40%]

Conventional Ventilator Unit

•

tOA

Outdoor air

condition in

winter

Dry bulb temperature (°F)

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 energy recovered is 0 kcal and the Ventilation load is (16.6 – 2.1) × 0.0749 × 600 = 651.6 Btu/min = 11.5 kW

tSA

56.8

Room air condition

of the Lossnay

Supply air condition

tRA

in winter

XSA 0.0047

XOA 0.0018

Absolute humidity (Ib/Ib’)

RA 0.0073

U-23

Page 33

CHAPTER 3 • General Technical Considerations

2. Calculating Lossnay Cost Savings

Use the following pages to assess the economical benefits of using the Lossnay in particular applications.

(1) Conditions

Return air volume (RA) = CFM (m3/hr)

•

Outdoor air volume (OA) = CFM (m3/hr)

•

Air volume ratio (RA/OA) =

•

Air conditions

•

Season Winter Heating Summer Cooling

Dry bulb

Item

Outdoors

Indoors

Operation time: Heating = hours/day × days/month × months/year = hours/year

•

Cooling = hours/day × days/month × months/year = hours/year

Energy: Heating = Type: Electricity Cost: dollar/kWh

•

Cooling = Type: Electricity Cost: dollar/kWh Power rates: Winter: dollar/kWh Summer: dollar/kWh

temp.

DB [°F] [°C]

Wet bulb

temp.

[°F]

[°C]

Relative

humidity

RH [%] [%]

Absolute humidity

[Ib/Ib’]

[kg/kg’]

Enthalpy

i kJ/kg

(Btu/Ib)

(kcal/kg’)

Dry bulb

temp.

[°F]

[°C]

Wet bulb

temp.

WB [°F]

[°C]

Relative

humidity

RH [%] [%]

Absolute

humidity

[Ib/Ib’]

[kg/kg’]

Enthalpy

i kJ/kg

(Btu/Ib)

(kcal/kg’)

(2) Lossnay Model

Model name:

•

Processing air volume per unit RA = CFM (m3/hr), OA = CFM (m3/hr), Air volume ratio (RA/OA) = CFM (m3/hr)

•

Energy recovery efficiency : Energy recovery efficiency = %,

•

Enthalpy recovery efficiency (cooling) = %, Enthalpy recovery efficiency (heating) = %

Static pressure loss (unit-type) RA= Pa OA = Pa (Note: Each with lters)

•

Power consumption (pack-type) = none because of unit type

•

(3) Indoor Blow Air Conditions

Heating Cooling

Temperature

[°F]

[°C]

[Btu/lb]

Enthalpy

[kJ/kg]

Data obtained from above equation and psychrometric chart

(Indoor temperature – outdoor air temperature) ×

energy recovery efficiency + outdoor air temperature

==(Indoor enthalpy – outdoor air enthalpy) ×

enthalpy recovery efficiency + outdoor air enthalpy

Dry-bulb temperature

•

Wet-bulb temperature

•

Relative humidity

•

Absolute humidity

•

Enthalpy

•

= = = = =

°F (°C) °F (°C)

Ib/Ib’ (kg/kg’)

Btu/Ib (kg/kg)

==Outdoor air temperature – (outdoor air

temperature – indoor temperature) × energy recovery efficiency

==Outdoor air enthalpy – (outdoor air

enthalpy – indoor enthalpy) × enthalpy recovery efficiency

Dry-bulb temperature

•

Wet-bulb temperature

•

Relative humidity

•

Absolute humidity

•

Enthalpy

•

= = = = =

°F (°C) °F (°C)

Ib/Ib’ (kg/kg’)

Btu/Ib (kg/kg)

U-24

Page 34

(4) Ventilation Load and Energy Recovery

Ventilation load without Lossnay (q1)

Ventilation load with Lossnay (q

Energy recovery (q

Ventilation load (%)

==Air specic gravity × ventilation volume

× (indoor enthalpy – outdoor air enthalpy)

Ventilation load (q × ( 1 – enthalpy recovery efficiency)

Air specic gravity × ventilation volume × (indoor enthalpy

–

or Ventilation load (q1)

× enthalpy recovery efficiency

Ventilation load = W = %

•

Ventilation load with Lossnay

•

= W = % Energy recovered = W = %

•

(5) Recovered Money (Power Rates)

Energy recovered: kW × Unit price $/kWh ×

Cost savings

dollar)

(

operation

Hr/year

time Hr/year = kW × $/

CHAPTER 3 • General Technical Considerations

Heating Cooling

==Air specic gravity × ventilation volume

× (outdoor air enthalpy – indoor enthalpy)

–

indoor blow enthalpy)

Heating Cooling

kWh

Ventilation load (q × ( 1 – enthalpy recovery efficiency)

Air specic gravity × ventilation volume × (indoor blow enthalpy

–

or Ventilation load (q1)

× enthalpy recovery efficiency

Ventilation load = W = %

•

ventilation load with Lossnay

•

= W = % Energy recovered = W = %

•

Energy recovered: kW × Unit price $/kWh × operation

Hr/year

time Hr/year = kW × $/

–

indoor enthalpy)

kWh

U-25

Page 35

CHAPTER 3 • General Technical Considerations

AEX-120-99—page 2

Figure 2. A psychrometric chart.

3. Psychrometric Chart

3.1 <US unit>

U-26

Page 36

3.2 <SI unit>

5.5

0.034

0.035

0.036

0.037

0.033

CHAPTER 3 • General Technical Considerations

Vapor pressure Pw [kPa]

0.00.000

0.1

0.005

0.004

0.5

0.001

0.002

0.003

0.92

/kg(DA)]

50494847464544434240 41393837363534333230 31292827262524232220 21191817161514131210 11987654320–1–2–3–4–9–10

5.0

4.5

4.0

3.5

3.0

2.5

2.0

1. 5

1. 0

Absolute humidity x [kg/kg(DA)]

0.006

0.007

0.008

0.009

0.010

0.011

0.012

0.013

0.014

0.015

0.016

0.017

0.018

0.019

0.020

0.021

0.022

0.023

0.024

0.025

0.026

0.027

0.028

0.029

0.030

0.031

0.032

0.96

0.95

0.94

Saturation [%]

0.93

Relative humidity [%]

Specific capacity v [m

Sensible heat ratio SHF

0.7

0.8

10000

15000

Wet bulb temperature t' [

Comparative enthalpy h [kJ/kg(DA)]

0.4

0.5

0.6

4500

5000

6000

7000

125

120

115

110

105

100

3800

3600

3400

3200

3000

2800

2600

2400

2200

2000

1800

1600

1400

1200

1000

C, atmospheric pressure 101.325 kPa)

(-10 to +50

Humid air psychrometric chart

Heat water ratio u = –– [kJ/kga]

1. 0

–10000

–20000

–40000

0.9

40000

20000

500

–500

–1000

–2000

–5000

0.3

3800

4000

4200

–7–8 –5–6 1

Dry bulb temperature t [°C]

0.75 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

Water

–5

Chilled

–1

–2

–4

–5

–8

U-27

Page 37

CHAPTER 3 • General Technical Considerations

4. Determining Lossnay Core Resistance to Bacterial Cross-

Contamination and Molds

Test Report

(1) Object

To verify that there is no bacterial cross-contamination from the outlet air to the inlet air of the Lossnay Core.

(2) Client

MITSUBISHI ELECTRIC CO. NAKATSUGAWA WORKS.

(3) Test Period

April 26, 1999 - May 28, 1999

(4) Test Method

The test bacteria suspension is sprayed in the outlet duct at a pressure of 1.5 kg/cm2 with a sprayer whose dominant particle size is 0.3 - 0.5 µm. The air sampling tubes are installed at the center of Locations A, B, C, D (see diagram below), in the Lossnay inlet/outlet ducts so that the openings are directly against the air ow, and then connected to the impingers outside the ducts. The impingers are lled 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.

Sprayer

Impinger

LOSSNAY Core

(5) Test Bacteria

The bacteria used in this test are as followed;

Bacillus subtilis: IFO 3134 Pseudomonas diminuta: IFO 14213 (JIS K 3835: Method of testing bacteria trapping capability of precision ltration lm elements and modules; applicable to precision ltration lm, 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 diminuta is shown in Table 2.

Impinger

HEPA Filter

Fan

Safety cabinet

U-28

Page 38

CHAPTER 3 • General Technical Considerations

Table 1 Test Results with

Bacillus Subtilis

(CFU/30L air)

No. A B C D

1 5.4 × 10

2 8.5 × 10

3 7.5 × 10

4 1.2 × 10

5 1.8 × 10

Average 2.0 × 10

Table 2 Test Results with

Pseudomonas Diminuta

(CFU/30L air)

5.6 × 10

7.5 × 10

< 10

1.2 × 10

1.5 × 10

< 10

No. A B C D

1 3.6 × 10

2 2.5 × 10

3 2.4 × 10

4 3.4 × 10

5 1.7 × 10

Average 2.7 × 10

2.9 × 10

1.2 × 10

7.2 × 10

8.4 × 10

3.8 × 10

4.7 × 10

< 10

(7) Considerations

Bacillus subtilis is commonly detected in the air and resistant to dry conditions. Pseudomonas diminuta is susceptible to dry conditions and only a few bacterium exists in the air; however, it is used to test lter performance because 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 Locations A and B in the outlet side duct where they are sprayed, but neither them are detected at Location C (in the air ltered by the HEPA lter) and Location D on the inlet side. Because the number of bacteria in Location A is substantially equal to one in Location B, it is estimated that only a few bacteria are present in the Lossnay Core on the outlet side. Also, no test bacteria are detected at Location D. The conclusion is, therefore, that the bacteria present in the outlet side will not pass through the inlet side even after the energy is exchanged.

Shunji Okada Manager, Biological Section Kitasato Research Center of Environmental Sciences

U-29

Page 39

CHAPTER 3 • General Technical Considerations

5. Lossnay Core Fire : retardant property

The Lossnay Core was also tested at General Building Research Corporation of Japan according to the fire retardancy test methods of thin materials for construction as set forth by JIS A 1322. The material was evaluated as a Class 2 flame retardant.

U-30

Page 40

CHAPTER 3 • General Technical Considerations

6. Lossnay Core Sound Reducing Properties Test

Because the Lossnay Core is made of many layers of plates and the permeable holes are extremely small, the core has outstanding sound reducing properties and is appropriate for ventilation in soundproof rooms. For example, LGH-100RX3-E has sound reducing characteristics of 35.0dB with a center frequency of 500Hz, which means that a sound source of 84.4dB can be shielded to 49.4dB.

Sound Reducing Effect Test Results

Test number

Name

Client

Address

Trade name

Main composition

Manufacture date

Size (unit : mm)

Test SpecimenTest Results

IVA-01-06

Mitsubishi Electric Corporation 1-3, Komaba-cho, Nakatsugawa-shi,

Gifu 508-8666, Japan

LGH-100RX

3-E

Air-to-Air Energy Recovery Ventilator

May 18, 2001

W1231 × H398 × D1521 (ANNEXED DRAWINGS No.1,2 show details.)

Joint adapter in the sound receiving room side (Portion A in ANNEXED DRAWING No.1) had

Note

been filled with oil clay and then covered with onefold aluminum tape, sound insulation sheet and glass wool around duct successively.

Date of test Sound transmitting size Air temperature, Relative humidity

Center

frequency

1000 1250 1600 2000 2500 3150 4000 5000

Average sound pressure level (dB)

87.0

Receiving

room Lr

59.3

62.8

61.0

58.7

58.3

57.0

54.3

49.4

50.7

48.7

47.7

47.4

47.0

48.2

48.8

47.6

(Hz)

100 125 160 200 250 315 400 500 630 800

Source

room Ls

83.3

83.8

85.5

86.0

86.1

85.0

86.2

84.4

84.7

85.5

89.2

89.3

90.7

92.8

83.4

95.0

May 18, 2001 Ф254 mm × 2

22.0∞C, 62%RH (Receiving room)

Level

difference D

24.0

21.0

24.5

27.3

27.8

28.0

31. 9

35.0

34.0

36.8

39.3

41.5

41.9

43.7

44.6

45.2

46.2

47.4

Equivalent

absorption

area in receiving

room A (m2)

2.65

3.21

3.69

3.48

3.54

3.96

4.40

4.62

4.80

5.06

5.58

6.26

7.03

7.57

8.62

10.19

12.42

15.51

Sound

transmission

loss

TL (dB)

9 12 12 12 16 18 17 20 22 24 23 25 25 25 25 26

Notes:

1. The graph shows level difference with (revised) sound transmission loss.

2. Test specimen area (Sound transmitting area) is: S = 0.10134m

(Ф254mm × 2) for calculating (revised) sound transmission

loss.

3. An arithmetic mean of revised sound transmission loss (1/3 octave, 125Hz

- 4000Hz)....18.4dB

Test method was determined according to JIS A 1416 : 1994 "Method for laboratory measurement of sound transmission loss" and Architectural Institute of Japan Standard "Measurement method on sound transmission loss of small

Standard

building elements".

(Reverberation room No. 2)

178.5m

180.0m

Test specimen

MIC.

Computer system

Printer

Chain block (2t)

Sound receiving side

Test specimen

Test Method

5560

Section

Test

laboratory

(Reverberation room No. 3)

300

Air layer (t50)

Sound source side

Neoprene rubber

Filled with sand

Cavity concrete block (t190) Filled inside with sand Mortared both sides (15mm)

F. L.

Volume

Fig. 1 Testing setup (Unit : mm)

Heat & Acoustics Laboratory, Building Physics Dept. General Building Research Corporation of Japan 5-8-1 Fujishirodai, Suita-shi, Osaka 565-0873, Japan

Revised sound

transmission

loss

TLc (dB)

Air-to-Air Energy

Recovery Ventilator

LGH-100RX

3-E

13 13 12 16 19 17

Level difference between the source room and the receiving room

20 22 24 23 25

Sound transmission loss (dB)

Revised sound transmission loss

25 25 25

Sound transmission loss

125 250 500 1000 2000 4000

Center frequency (Hz)

Iwao Kurahashi (Head)

Responsible parties

Ta kao Waki (Section chief) Mitsuo Morimoto (Section chief)

Sound source sideSound receiving side

Test specimen

SP.

Amplifier2 ch selector

EqualizerReal time analyzer

Noise generator

U-31

Page 41

CHAPTER 3 • General Technical Considerations

7. Changes in the Lossnay Core

An example of a building with Lossnay units installed, that has been used as a case study to assess the changes in the units.

7.1 Building Where Lossnay is Installed

(1) Building : Meiji Seimei, Nagoya Office/shop building

1-1 Shinsakae-machi Naka-ku, Nagoya

(2) No. of Floors : 16 above ground, 2-story penthouse, 4 basement oors

(3) Total Floor Space : 418,640 ft2 (38,893 m2)

(4) Reference Floor Space : 14,940 ft2 (1,388 m2)

7.2 Specications of Installed Ventilation Equipment

(1) Air Handling Method : 4 fan coil units (perimeter zone) per oor

Chilling Unit : Absorption-type 250 kT × 1 unit, turbo 250 kT × 2 units Gas Direct Heating/Cooling Boiler

(2) Ventilation Method : Air - air total energy recovery unit “Lossnay”

LS-200 × 18 units installed in penthouse. Outdoor air treatment volume: 27,211 CFM (46,231 CMH), Exhaust air treatment volume: 31,980 CFM (54,335 CMH).

(3) Lossnay Units Used : LS-200* (with four Lossnay Cores)

: 340 kT, heating 1,630 kW

Lossnay Duct System Diagram Diagram of Lossnay Penthouse Installation

Exhaust air

RA side

bypass damper

RA fan

(for exhaust)

OA side bypass damper

Lossnay

U-32

(for intake)

OA fan

Outdoor air

4080

1300 1300

3200

Lossnay

4300

Lossnay

2000

700

O A

10040

Unit (mm)

Page 42

CHAPTER 3 • General Technical Considerations

7.3 Lossnay Operation

(1) Unit Operation Began : September 1972

Daily Operation Began : 7:00 Daily Operation Stops

: 18:00

Average daily operation: 11 hours

}

(2) Inspection Date : November 1983

(3)

Months When Units are in Bypass Operation

: Three months of April, May, June

(4) Total Operation Time : (134 – 33) months × 25 days/month × 11 hours/day = 27,775 hours

7.4 Changes Detected in the Lossnay Core

Two Lossnay Cores were removed from the 18 Lossnay LS-200 installed, and static pressure loss and exchange efficiencies were measured. See chart on right that compares initial operation to same unit 11 years later. The appropriate air volume for one Lossnay Core was 300 CFM (500 m point was ±120 CFM (±200 m

/hr) of that value.

/hr), and the measurement

Characteristics in change of Lossnay Core over time

Enthalpy recovery efficiency during heating

300

(1.20)

Heat recovery efficiency

Data from delivery (1974) Data from 1983

200

(0.80)

100

(0.40)

Static pressure loss (Pa)

(Static pressure loss (inH2O)) Recovery efficiencies (%)

300

(180)

Treated air volume

Static pressure loss

500

(300)

700

(420)

CMH

(CFM)

7.5 Conclusion

(1) Changes in the the Lossnay Core after approximately 11 years of use and an estimated 28,000 operation hours were not

found. The static pressure loss was 0.60 to 0.64 in H

2O at 300 CFM (150 to 160 Pa at 500 m

Pa) increase. The exchange efficiencies had decreased slightly to above 300 CFM (500 m3/hr), however, this is considered to be insignicant and remained in the measurement error range.

(2) The Core surface was black with dust, but there were no gaps, deformed areas, or mold that would pose problems during

practical use.

/hr), which was a 0.04 in H2O (10

U-33

Page 43

CHAPTER 3 • General Technical Considerations

8. Comparing Energy Recovery Techniques

Basic Methods of Total Energy Exchangers

Country of

Type Method Air ow development Static Conductive Cross-ow Japan

Energy recovery (Mitsubishi Lossnay) transmission type principle

Rotary type Heat accumulation/ Counterow Sweden humidity accumulation type

8.1 Principle Construction of Rotary-type Energy Recovery Techniques

Rotary-type energy recovery units have a rotor that has a layered

•

honeycomb structure made of kraft paper, plastic, aluminum or other substrate materials, drive motor and housing.

A moisture absorbent material (desiccants such as litium

chloride, silicagels or engineered molecular sieve material) is applied onto the rotor, and humidity is transferred. The rotor rotates a few to 30 times a minute by the drive motor.

Approx. ø1.5mm

Exhaust

Fresh air

Rotary-type energy recovery units, when cooling, the high

•

temperature and high humidity ventilation air passes through the rotor, with the heat and humidity being absorbed by the rotor. When the rotor rotates, it moves into the exhaust air passage, and the heat and humidity is discharged to the outdoors because the exhaust is cool and has low humidity.

The rotor rotates and returns to the ventilation air passage to

absorb the heat and humidity again.

Function of the purge sector

•

There are two separation plates (purge sectors) in the front and

back of the rotor to separate airow. Because one of the plates is slightly shifted, part of the ventilation air always ows into the exhaust air passage to prevent the exhaust air and ventilation air from mixing. (A balanced pressure difference is required.)

Purge sector

Drive motor

Rotor

Supply air Fresh air

Bearing

Return air Exhaust

Rotor rotation direction

Drive motor

Purge sector

Room side

Fresh air

U-34

Return air

When a purge sector is added, the exhaust air in the rotor going into the air on the supply side can be prevented. Vr: Rotor speed, Vs: Air speed in relief section

Page 44

CHAPTER 3 • General Technical Considerations

8.2 Comparing Static-type and Rotary-type Energy Recovery Units

Specication. Static-type Rotary-type

Conductive transmission-type: cross-ow

Static-type transmission total energy recovery unit with orthogonally layered honeycomb-shaped treated plates

Construction/ Principle

Moving Parts

Material Quality Engineered resin composite Plastic, aluminum plates, etc.

Prelter Required (periodic cleaning required Required (periodic cleaning required)

Element Clogging

Air Leakage Gas Transmission Rate

Bacteria Transmission Rate

Bypass air pass for comfortable season

Maintenance

Life

Model is Available

Measure of useability

formed into multiple layers.

As the supply air and exhaust air pass through different

•

passages (sequentially layered), the air passages are completely separated.

None

•

Fixed core

Occurs (State where dirt adheres onto the element air

•

passage surface; however, this is easily removed with a vacuum cleaner.)

Approximately 2.5% air leak at standard fan position.

Leaks found on the air supply side can be reduced to 0 by leaking the loss air volume (approx. 10%) on the exhaust side with the fan position to the core.

Gas transmission ( Ammonia : approx. 2.9%)

•

In certied EATR on AHRI, Mitsubishi core EATR is

0%. Wheel types EATR are 0.04-7.7%.

Low (Because air intake/exhaust outlets are separate,

•

transmission is low.)

Bypass circuit required (Permitted on one side of air intake and exhaust air outlet passage)

Core cleaning: More than once a year The core surface will clog with lint and dirt, but cleaning is easy with a vacuum cleaner. Only the two core air passage intakes need to be cleaned.

Core: Semi-permanent (10 years or more)

Static-type units do not break.)

Available from small to large.

Characteristic design of small

possible.

Large models are easy to

layout

: High o : Average × : Poor

•

and medium models are

match to a machine room

Heat accumulation/humidity accumulation-

type: counterow The rotor core has honeycomb-shaped kraft paper, etc., to which a moisture absorbent is applied (lithium chloride, etc.). The rotor rotates, and heat accumulation/humidity accumulation - heat discharge/ humidity discharge of total energy exchange is performed by passing the exhaust and intake airows into a honeycomb passage.

× Supply air and exhaust airows go into the same air

passage because of the rotary-type construction.

× Rotor driven with belt by gear motor

Rotor core

Occurs (Dust is smeared into element air passage lter.) (The dust adhered onto the core surface is smeared into the air passage by the purge sector packing. It cannot be removed easily and thus the air volume decreases.)

× Purged air volume occurs

To prevent exhaust leaking to the air intake side, a purge air volume (6 to 14%) leak is created on the exhaust side. Thus, there are problems in the purge sector operation conditions (pressure difference, speed), and the air volume must be balanced.

Gas transmission ( Ammonia : 45-57%)

× High (Because air intake/exhaust outlets are the same,

transmission is high.)

Bypass circuit required (Required on both air intake

and exhaust air outlet sides) (Theoretically, bypass operation is possible by stopping the rotation, but the core will over-absorb and cause serious damage.)

Core

cleaning: Once or twice a year Cleaning is difficult as dust is smeared into core by the purge sector packing.

× Gear motor for rotor drive : Periodic inspection × Rotor bearing, rotor drive belt : Periodic inspection

Core: Semi-permanent (10 years or more)

(Periodic replacement is required because of the rotor bearings and the core clogging.)

× Rotor drive belt : Periodic replacement × Drive motor, rotor bearing : Periodic replacement

Large type only × Small models are difficult to design because of the

rotor magnitude.

U-35

Page 45

Page 46

CHAPTER 4

Characteristics

CHAPTER 4 • Characteristics

U-37

Page 47

CHAPTER 4 • Characteristics

1. How to Read the Characteristic Curves

1.1 Obtaining Characteristics from Static Pressure Loss

(1) Static pressure loss from a straight pipe duct length (at required air volume)

(2) Static pressure loss at a curved section (at required air volume)

(3) Static pressure loss of related parts (at required air volume)

Total static pressure loss

Static pressure loss at

application point

Total static

pressure loss

Static

pressure

Required air

volume

Estimated static pressure loss curve obtained from

Air volume at application point

and

Intersection with air volume static

pressure characteristic curve

Air volume

2. Calculating Static Pressure Loss

2.1 How to Read the Air Volume - Static Pressure Curve

It is important to know the amount of static pressure loss applied onto the Lossnay when using ducts for the air distribution. If the static pressure increases, the air volume will decrease. The air volume - static pressure curve (Q-H curve) example shows the percentage at the decrease. A static pressure of 0.08 in H2O (19.6 Pa) is applied to Point A, and the air volume is 300 CFM (500 m3/ h). The duct resistivity curve shows how the static pressure is applied when a duct is connected to the Lossnay. Thus, the L =

32.7 ft (9.97 m) duct resistivity curve in the diagram shows how the static pressure is applied when a 32.8 ft (10 m) duct is connected. Intersecting Point A on the Lossnay Q-H curve is the operation point.

Example

Static pressure

0.08 in H (19.6 Pa)

Duct resistivity curve

Air volume

Q-H curve

300CFM

(500 m

L = 32.8 ft (10 m)

/h)

Duct Resistivity Curve

Duct Static Pressure

When duct is long Increases

If length is the same but the air volume Increases increases

If the duct diameter is narrow Increases

If the duct inner surface is rough (such as a spiral)

U-38

Increases

(Duct length)

64 ft (20 m)

48 ft (15 m)

33 ft (10 m)

Static pressure

Air volume

16 ft (5 m)

Page 48

CHAPTER 4 • Characteristics

Reference

Pressure loss caused by outdoor air wind velocity (inH2O)

= 0.003019 × r × V2

r : Air weight 0.0749 Ib/ft

{

v : Velocity (ft/s)

0.7

0.6

0.5

0.4

0.3

0.2

0.1

Outdoor air pressure loss (inH2O)

0102030405060

Outdoor air (ft/s)

Reference

Pressure loss caused by outdoor air wind velocity (Pa)

r = 2 2

r : Air weight 1.2 kg/m

{

v : Velocity (m/s)

× V2 =

1.2 × (velocity)

180 160 140 120 100

60 40 20

Outdoor air pressure (Pa)

2 4 6 8 10 12 14 16 18

Velocity (m/s)

U-39

Page 49

CHAPTER 4 • Characteristics

2.2 Calculating of Duct Pressure Loss

(1) How to Calculate Curved Sections in Ductwork

Table 6. Pressure Losses in Each Duct Area

Length of

Equivalent

No.

Duct Area

90°

Smooth Elbow

Rectangular

Radius Elbow

Rectangular Vaned

Radius Elbow

90°

Miter Elbow

Rectangular

Square Elbow

Rectangular Vaned

Square Elbow

Rectangular Vaned

Square Junction

Rectangular Vaned

Radius Junction

45°

Smooth Elbow

10 Expansion

11 Contraction

Outline Diagram

0.75

Value

0.73

0.38

0.26

0.17

0.15

Conditions

R/D = 0.5

= = 1.0 = 1.5 = 2.0

W/D R/D

0.5

1.30

0.75

1. 0

1. 5

0.5

0.75

1. 0

1. 5 R/D

0.5

0.75

1. 0

1. 5

0.5

0.75

1. 0

1. 5

0.47

0.28

0.18

0.95

0.33

0.20

0.13

0.70

0.16

0.13

0.12

0.45

0.12

0.10

0.15

0.5

1-3

No. of vanes

0.87 53D

1.25 76D

0.35 21D

Same loss as circular duct. Velocity is based on inlet.

With or without vanes, rectangular or round

a = 5°

Loss is for hV1 - hV

10° 20° 30° 40°

1/2 times value for similar 90°

0.17

0.28

0.45

0.59

0.73

a = 30°

0.02

45°

60° Loss is for V

0.04

0.07

Round

Pipe

43D 23D 15D 10D

79D 29D 17D

11D 57D 20D 12D

42D 10D

8D 7D

27D

7D 6D 9D

10D 17D 27D 36D 43D

1D 2D 4D

No.

Length of

Equivalent

Duct Area

Outline Diagram

Conditions

Value

Round

Pipe

12 Transformer 0.15 9D

14° or less

Short

Entrance

Short

Exit

Bell-shaped

Entrance

Bell-shaped

Exit

Re-entering

inlet

Sharp edge,

round orifice

V1/V2 = 0

0.25

0.50

0.75

0.50 30D

1. 0 60D

0.03 2D

1. 0 60D

0.85 51D

2.8

2.4

1. 9

1. 5

1. 0

170D 140D

110 D

90D

60D Loss is for V2

0.02

1/V2

20° 40° 60° 90°

120°

20° 40° 50° 90°

120°

= 0

0.25

0.50

0.75

0.03

0.05

0.11

0.20

0.03

0.08

0.12

0.19

0.27

0.5

0.45

0.32

0.18

30D

27D

19D

11D

Pipe inlet (with circular hood)

Pipe inlet (with rectangular hood)

Short contraction

Loss is for V

60D

= 0

0.20

0.40

0.60

0.80

1. 0

0.64

0.36

0.16

0.04

39D

22D

9D 2D

Short expansion

1/V2

Loss is for V

Suction inlet (punched narrow plate)

Free are ratio

0.2

0.4

0.6

0.8

7.6

3.0

1.2

U-40

Page 50

CHAPTER 4 • Characteristics

3. How to Obtain Efficiency from Characteristic Curves

How to Read Characteristic Curve

Recovery efficiency

Static pressure outside unit

Temperature

recovery efficiency

Recovery efficiency

Static pressure outside unit

Obtaining the efficiency when supply air and exhaust air volumes are different.

•

Enthalpy recovery efficiency

Total static pressure loss (or total straight pipe equivalent length)

High notch air volume

Low notch air volume

(heating)

(cooling)

Static pressure loss related parts (straight pipe equivalent length total)

Pipe length

The efficiency obtained from the intake side air volume in each characteristic curve can be corrected with the air volume ratio

in the bottom right chart.

If the intake side and exhaust side duct lengths are greatly different or if a differential air volume is required, obtain the intake

side efficiency from the bottom right chart.

Energy Recovery Efficiency Correction Curve

Exhaust air volume Supply air volume

1. 21.3

0.8 0.9 1. 01.1 1. 4

Efficiency obtained with air volume on supply side from characteristic curve

Air volume ratio = Supply air volume

Exhaust air volume

Energy recovery

efficiency

(%)

Air volume ratio =

0.5 0.6 0.7

Supply side efficiency

after correction

Efficiency obtained from supply side air volume (%)

50 60 70 80 90 10 0

Corrected energy recovery efficiency (%)

U-41

Page 51

CHAPTER 4 • Characteristics

4. Sound

Sound is vibration transmitted through an object. The object that vibrates is called the sound source, and energy that is generated at the source is transmitted through the air to the human ear at certain frequencies.

4.1 Sound Levels 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 is different according to the strength of the sound and the frequency, and the relation to the tone (see chart 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 detected by the human ear, the strength of sound that can be detected that is equivalent to a 1,000 Hz sound is obtained for each frequency. The point where these 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 detects sounds that are less than 1,000

•

Hz as rather weak, and sounds between 2,000 to 5,000 Hz as strong.

ISO Audio Perception Curve

120 dB

Sound level (dB)

Minimum audible valve

Frequency (Hz)

100

4.2

–200

–20

–2

–0.2

–0.02

–0.002

–0.0002

Sound

pressure

(Pa)

Sound

strength

(W / cm

)

4.2 How to Measure Sound Levels

A sound level meter (JIS C 1502, IEC 651) is used to measure sound levels and has three characteristics (A*1, C*2 and Flat) as shown on the right. These represent various sound wave characteristics. Generally, Characteristic A, which is the most similar to the human ear, is used. The value measured with the Lossnay unit operating includes noise caused by the unit and background noise*3.

*1. Characteristic A is a sound for which the low tones have been adjusted to be similar to the auditory perception of the human ear. *2. Characteristic C is a sound for which the high and low tones have been adjusted slightly. *3. Background noise: any sound present in the target location when no sound is being produced.

Characteristic A

Response (dB)

Characteristic C

Flat characteristic

Frequency (Hz)

U-42

Page 52

CHAPTER 4 • Characteristics

4.3 Sound Frequency Analysis

The human ear detects sound differently according to the frequency; however, the sound generated from vibrations is not limited to one frequency, but instead, various frequencies are generated at different levels. NC curve will show how the various frequencies are generated at different levels, which is determined according to the difficulty of detecting conversations.

Even if the sound is a very low level, it can be detected if it has a specic and loud frequency.

•

These sounds are low during product design stages, but sounds may become very disturbing if resonating on ceilings, walls,

etc.

Example: Continuous Frequency Analysis NC Curve

Level (dB)

Frequency (Hz)

Tolerable Sound Levels and NC Values According to Room Application

•

Room Application

Broadcasting studio 25 15 - 20 Cinema 40 30

Music hall 30 20 Hospital 35 30

Theater (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

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

NC Value Room Application

SPL (dB)

Min. audible limit

Frequency band (Hz)

NC Value

U-43

Page 53

CHAPTER 4 • Characteristics

* Approximate values of sound levels using practical examples The following diagram shows typical everyday sounds. Approximate degree of sound levels can be seen. * Sound levels and perception

Boiler making Forging, riveting, drilling

Grinder

Engine, large motor

Loud factory

Factory

Normal machine factory

Office

Computer room

Typing room

Many occupants

Few occupants

Transportation facilities

Residential area

Subway

Overhead train

Passenger car

Business and industrial district

Suburb

Quiet night

(dB) 130 Painful to ears 120 Near a airplane engine

110 Slight pain to ears Automobile horn (2 m away) 100 Too loud want to cover Train with open ears window in tunnel

90 Conversation with the Tr ain passing on person near you is overhead tracks not possible 80 Conversation is not Train passing through possible unless voice is shopping district raised 70 Voice is raised Shopping district with intentionally to converse heavy traffic

60 Loud, but normal In busy office conversation is possible

50 Sound is audible and Among quiet group disturbing of pedestrians

40 Quiet but not peaceful In quiet group of

Conversation

people

30 Peaceful In broadcasting studio

20 Very quiet Sound of leaves brushing against 10 each other 0 Source: “Heibon Sha, Industrial Encyclopedia”

U-44

Page 54

4.4 Indoor Sounds

(1) Indoor Sounds Principles

1) Power Levels The Power level of the sound source (PWL) must be

understood when considering the effects of sound. See formula below to obtain PWL from the measured sound pressure data in an anechoic chamber.

CHAPTER 4 • Characteristics

Fig. 1.

Unit

PWL = SPLo + 20 log (

PWL : Sound source power level (dB) SPLo : Measured sound pressure in anechoic

chamber (dB)

ro : Distance from the unit to measuring point (ft,m)

2) Principal Model Consider the room shown in Figs. 1 and 2.

Fig. 1 shows an example of an integrated unit (similar to a

•

cassette-type Lossnay unit) and supply air diffuser (with return grille).

Fig. 2 shows an example of a separated unit (similar to a

ceiling-embedded type Lossnay unit) and supply air diffuser (with return grille).

is the direct sound from the supply air diffuser (return

•

grille), and is the echo sound. ( to ) is the direct sound emitted from the unit and duct that can be detected through the nished ceiling. is the echo sound of .

3) Position of Sound Source and Sound Value

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

ro) + 11 [dB] ...................(I)

{ }

4πr

Supply air diffuser (return grille)

Fig. 2.

Unit

Supply air diffuser (return grille)

Fig. 3.

(Position of Sound Source and Directivity Factor Q)

(i) (ii)

SPL : PWL : Power level of sound source [dB] Q : Directivity factor (Refer to Fig. 3) r : Distance from sound source [ft,m] R : Room constant [R =

α

S : Total surface area in room [ft2,m2]

Sound pressure level at reception point [dB]

S/(1 – α)]

: Average sound absorption ratio in room

(Normally, 0.1 to 0.2)

Position of Sound Source Q

a Center of room 1

b Center of ceiling 2

c Edge 4

d Corner 8

U-45

Page 55

CHAPTER 4 • Characteristics

For the supply air diffuser (and return grille) in Fig. 2, PWL

•

must be corrected for the sound transmission loss from the duct work (TL) such that:

PWL’ = PWL – TL

Item (i) in formula (II) page 48 is the direct sound ( , ),

•

and (ii) is the echo sound ( , ).

The number sources of sound 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 = 10 log (10

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 frequency band, and calculated values are combined by formula (III) for an accurate value. (When A-range overall value is required, subtract A-range correction value from calculated values of formula (II), and then combine them by formula (III).)

SPL1/10

+ 10

SPL2/10

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

)

(2) Reducing Lossnay Unit Operating Sound

1) When the airow of the unit from above the ceiling is the sound source.

(See page 48: Fig. 1 , , Fig. 2 to , )

(A) Do not install the unit using the following specications if

disturbing sound could be emitted from large units. (Refer to Fig. 4) a) Decrease in diameters in the ductwork:

(Ex. 10"dia(ø 250) → 6"dia(ø 150), 8"dia(ø 200) → 4"dia(ø 100)) b) Curves in aluminum exible ducts, etc. (Especially if immediately installed after unit outlet) c) Opening in ceiling panels d) Hanging the unit on materials that cannot support

the wight.

(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 high). b) Adding of soundproofing materials to areas below

the source of the sound. (The entire surface must be covered with

soundproofing sheets. Note that in some cases,

covering the area around the unit may not be

possible due to generated heat.)

Transmission Loss in Ceiling Material (dB) Example

Material

( ) indicates

thickness

Average 20 22 23

125 10 12 20

250 11 15 21

500 19 21 23

1,000 26 28 26

2,000 34 35 24

Frequency band (Hz)

(III)

4,000 42 39 —

Fig. 4. Large Unit Installation (Example)

Fig. 5. Countermeasure (Example)

Plaster Board

1/4 inch

7 mm

( ) ( ) ( )

a) d)

a) b)

Plaster Board

3/8 inch

9 mm

c) b)

Lauan Plywood

1/2 inch

12 mm

U-46

Page 56

When supply air diffuser (and return grille) is the source of the sound Part 1

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

(and return grille) as shown in Fig. 6, installing an a) silencer box, b) silence duct or c) silence grille is recommended.

(B) If sound is being emitted from the supply air diffuser (and

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

When supply air diffuser (and return grille) is the source of the sound 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, add soundproofing material that has a high sound absorbency as shown in Fig. 8 a). This is not, however, very effective with direct sounds.

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

shown in Fig. 8 b) is effective with sound emitted from center of the room, but will be inadequate towards sound emitted from corner of the room.

CHAPTER 4 • Characteristics

Fig. 6 Sound from Supply Air Diffuser

a) b) c)

Fig. 7 Countermeasure (Example)

a) b)

Fig. 8 Additional Countermeasure (Example)

a) b)

U-47

Page 57

CHAPTER 4 • Characteristics

5. NC Curves

LGH-F300RX5-E

Background noise : 25 dB or less (A range) Background noise : 25 dB or less (A range) Measurement site : Anechoic chamber Measurement site : Anechoic chamber Operation conditions : Lossnay ventilation Operation conditions : Lossnay ventilation Power supply : 208 V 60 Hz Power supply : 230 V 60 Hz

Extra high

High

Low

Octave band sound pressure level (dB)

Extra Low

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

Octave band frequency near center (Hz)

NC-10

NC-20

NC-70

NC-60

NC-50

NC-40

NC-30

1.5 m below Measurement

point

LGH-F470RX5-E

Extra high

High

Low

Octave band sound pressure level (dB)

Extra

Low

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

Octave band frequency near center (Hz)

NC-10

NC-70

NC-60

NC-50

NC-40

NC-30

NC-20

1.5 m below Measurement

point

Extra high

High

Low

Octave band sound pressure level (dB)

Extra

Low

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

Octave band frequency near center (Hz)

Extra

high High

Low

Extra

Octave band sound pressure level (dB)

Low

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

Octave band frequency near center (Hz)

NC-20

NC-10

NC-20

NC-10

NC-70

NC-60

NC-50

NC-40

NC-30

NC-70

NC-60

NC-50

NC-40

NC-30

1.5 m below

Measurement point

LGH-F600RX5-E

Extra high

High

Low

Extra

Octave band sound pressure level (dB)

Low

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

Octave band frequency near center (Hz)

NC-70

NC-60

NC-50

NC-40

NC-30

NC-20

NC-10

U-48

1.5 m below Measurement

point

Extra high

High

Low

Extra

Octave band sound pressure level (dB)

Low

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

Octave band frequency near center (Hz)

NC-20

NC-10

NC-70

NC-60

NC-50

NC-40

NC-30

1.5 m below Measurement

point

Page 58

CHAPTER 4 • Characteristics

LGH-F1200RX5-E

Extra high

High

Low

Octave band sound pressure level (dB)

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

Octave band frequency near center (Hz)

NC-10

NC-70

NC-60

NC-50

NC-40

NC-30

NC-20

1.5 m below Measurement

point

Extra

high High

Low

Octave band sound pressure level (dB)

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

Octave band frequency near center (Hz)

NC-10

NC-20

NC-70

NC-60

NC-50

NC-40

NC-30

1.5 m below Measurement

point

U-49

Page 59

Page 60

CHAPTER 5

System Design Recommendations

Page 61

CHAPTER 5 • System Design Recommendations

1. Lossnay Unit Operating Environment

Main Unit Installation Conditions OA ( Outdoor Air ) conditions RA ( Return Air ) conditions

Commercial use

Lossnay

Pay special attention to extreme operating conditions.

14°F to 104°F

-10°C to 40°C

RH80% or less

1.1 Cold Weather Area Intermittent Operation

When the OA temperature falls below 14°F (-10°C) during operation, the SA-fan will change to intermittent operation. OFF for 10 minutes, ON for 60 minutes.

1.2 In Cold Climates with Outdoor Temperature of 23°F (–5°C) or Less

Plot the Lossnay intake air conditions A and B on a psychrometric chart (see right). If the high temperature side air B intersects the saturation curve such as at C, moisture condensation or frost will build on Lossnay. In this case, the low temperature side air A should be warmed up to the temperature indicated by Point A’ so that Point C shifts to the Point C’.

5°F to 104°F

-15°C to 40°C

RH80% or less

14°F to 104°F

-10°C to 40°C

RH80% or less

Saturation curve

Dry bulb temperature (°F,°C)

C’

A’

Absolute humidity (kg/kg’)

1.3 In High Humidity Conditions with Relative Humidity of 80% or More

When using the system in high humidity conditions such as heated indoor pools, bathrooms, mushroom cultivation houses, high-fog areas etc., moisture will condense inside the Core, and drainage will occur. Lossnay units should not be used in these types of applications.

1.4 Other Special Conditions

Lossnay units cannot be installed in locations where toxic gases and corrosive elements such as acids,

•

alkalis, organic solvents, oil mist or paints exist.

Cannot be installed where heat is recovered from odiferous air and supplied to another area.

•

Avoid installing in a location where unit could be damaged by salt or hot water.

•

U-52

Page 62

CHAPTER 5 • System Design Recommendations

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

The sound levels specified for Lossnay units are generated from tests conducted in an anechoic chamber. The sound levels may increase by 8 to 11 dB according to the installation construction material and room contents. When using Lossnay units in a quiet room, it is recommended silencer duct, silencer intake/exhaust grill or silencer box be installed.

3. Attaching Air Filters

An air filter must be mounted to both the intake and exhaust air inlets to clean the air and to prevent the Core from clogging. Periodically clean the filter for optimum Lossnay unit performance.

4. Constructing the Ductwork

Always add insulation to the two ducts on the outdoor side (outdoor air intake and exhaust outlet) to prevent frost or

•

condensation from forming.

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

•

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

•

(A deep hood is recommended.)

5. Bypass Ventilation

Do not operate “bypass ventilation” when heating during winter. Frost or condensation may form on the main unit.

6. Night purge function

Do not use the night purge function if fog or heavy rain is expected. Rain water may enter the unit during the night.

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

Measurement

Conditions

Measurement method

• Photoacoustic

Spectroscopy (PAS) for SF

•

Non-dispersive Infrared Detector (NDIR) for CO

•

Gas Detector Tube for others

The fans are positioned at the air supply/exhaust suction positions of the Lossnay Core

Measurement conditions:

80.6°F (27°C), 65% RH

* OA density for CO2 is 600 ppm.

Gas

Isopropyl alcohol 1. 0 2,000 50 2.5 400

Ammonia 1. 0 70 2 2.9 50

Carbon dioxide 1.0 44,500 1,400 1. 8

Sulfur hexauoride 1. 0 27.1 0.56 2.1

Air Volume

Ratio

QSA/QRA

Exhaust Air

Concentration

CRA (ppm)

Supply Air

Concentration

CSA (ppm)

Transmission

Rate

(%)

Concentrations

Max. Workplace

(ppm)

U-53

Page 63

CHAPTER 5 • System Design Recommendations

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

Main

Generation

Site

Chemical plant or chemical laboratory

Toilet

Others

Air (reference)

: Recommended : Not recommend × : Avoid

Gas

Sulfuric acid H

Nitric acid HNO

Phosphoric acid H

Acetic acid CH

Hydrogen chloride HCl Gas Toxic 427 58 427 58 5 ×

Hydrogen uoride HF Gas Toxic 90 90 0.6 ×

Sulfur dioxide SO

Hydrogen sulde H2S Gas Toxic 2.3 2.3 10

Ammonia NH3 Gas Bad odor 635 40 635 40 50 ×

Phosphine PH

Methanol CH3OH Vapor Toxic

Ethanol CH3CH2OH Vapor Toxic

Ketone Vapor Toxic

Skatole C

Indole C9H7N Gas Bad odor Minute Minute

Ammonia NH3 Gas Bad odor 635 40 635 40 50 ×

Nitric monoxide NO 0.0043

Ozone O3

Methane CH4

Chlorine Cl2

Air Mixed gases Gas Non-toxic

Oxygen O2 Gas Non-toxic

Nitrogen N2 Gas Non-toxic

Carbon monoxide CO Gas Toxic

Carbon dioxide CO2 Gas Non-toxic 0.759 0.759

Molecular

Formula

2SO4 Mist Toxic 2,380 2,380 0.25 ×

3 Mist Toxic 180 180 10 ×

3PO4 Mist Toxic 41 41 0.1 ×

3COOH Mist Bad odor 2,115 2,115 25 ×

2 Gas Toxic 32.8 32.8 0.25

3 Gas Toxic 0.26 0.26 0.1

9H9N Gas Bad odor Minute Minute

Gas

Type

Hazardous

level

Solubility in Water

US unit SI unit

/ft3Ib/100Ib

Soluble Soluble

0.0301 0.0301

Minute Minute

0.0167 0.0167

0.0283 0.0283

0.0143 0.0143

0.0214 0.0214

mℓ/mℓ

0.0043

0.00139 0.00139

g/100g

Max.

Workplace

Concentration

200

1,000

0.1

0.5

Useability

of Lossnay

Note: 1. Lossnay should not be used in environments with water soluble gases and mists because the amount that is

transmitted with the water is too high.

2. Lossnay should not be used in environments with acidic gases and mists because these will accumulate in the Core

and cause damage.

3. The table data above apply to only Lossnay partiton plate of total energy recovery units.

U-54

Page 64

CHAPTER 5 • System Design Recommendations

9. Automatic Ventilation Switching (Refer to technical manual (Control) page C-40)

Effect of Automatic Ventilation Mode

The automatic damper mode automatically provides the correct ventilation for the conditions in the room. It eliminates the need for manual switch operations when setting the Lossnay ventilator to “bypass” ventilation. The following shows the effect “bypass” ventilation will have under various conditions.

(1) Reduces Cooling Load

If the air outside is cooler than the air inside the building during the cooling season (such as early morning or at night), “bypass” ventilation will draw in the cooler outside air and reduce the cooling load on the system.

(2) Cooling Using Outdoor Air

During cooler seasons (such as between spring and summer or between summer and fall), if the occupants in a room cause the temperature of the room to rise, “bypass” ventilation will draw in the cool outside air and use it as is to cool the room.

(3) Night Purge

“Bypass” ventilation can be used to release hot air from inside the building that has accumulated during the hot summer season. LGH-RX5-E series has night purge function, that is used in the summer to automatically ventilate a room at night while the air conditioner is stopped, to discharge accumulated heat and thereby reduce the air conditioning load the next morning. (Selectable function)

(4) Cooling the Office Equipment Room

During cold season, outdoor air can be drawn in and used as is to cool rooms where the temperature has risen due to office equipment use. (Only when interlocked with City Multi and M-Series or P-Series indoor units.)

U-55

Page 65

CHAPTER 5 • System Design Recommendations

10. Alternate Installation for Lossnay

10.1 Top/bottom Reverse Installation

All LGH-RX5 models can be installed in top/bottom reverse.

Top

Bottom

Top

10.2 Vertical and Slanted Installation

All LGH-RX5 models should not be used in both vertical and slanted installation to avoid any problems (motor noise, water incoming etc).

U-56

Page 66

CHAPTER 5 • System Design Recommendations

11. Installing Supplementary Fan Devices

On occasions it may be necessary to install additional fans in the ductwork following LGH-type Lossnay units because of the addition of extra components such as control dampers, high-efficiency filters, sound attenuators, etc. which create a significant extra static pressure to the airflow. An example of such an installation is as shown below.

Static pressure generating component Additional fan

SA RA

Lossnay fan

Lossnay

For such an installation, avoid undue stress on the fan motors. Referring to the diagrams below, Lossnay with extra fans should be used at the point of left side from A.

Q-H for Lossnay Without Extra Fan Q-H for Lossnay With Extra Fan

(Static pressure) (Static pressure)

Lossnay specication curve

Extra fan specication curve

Lossnay with extra fan

Lossnay with static pressure increasing component.

Lossnay specication curve

H1 + H2

Lossnay with static pressure increasing component.

Lossnay without static pressure increasing component.

(Air volume) (Air volume)

Q1 Q1’

U-57

Page 67

Page 68

CHAPTER 6

Examples of Lossnay Applications

Page 69

CHAPTER 6 • Examples of Lossnay Applications

This chapter proposes Lossnay ventilation systems for eight types of applications. These systems were planned for use in Japan, and actual systems will differ according to each country - the ventilation systems listed here should be used only as reference.

1. Large Office Building

1.1 System Design Challenges

Conventional central systems in large buildings, run in oor and ducts, had generally been preferred to individual room units; thus, air conditioning and ventilation after working hours only in certain rooms was not possible. In this plan, an independent dispersed ventilation method applied to resolve this problem. The main advantage to such a system was that it allows 24-hour operation. A package-type indoor unit of air conditioner was installed in the ceiling, and ventilation was performed with a ceiling-embeddedtype Lossnay. Ventilation for the toilet, kitchenette and elevator halls, etc., was performed with a straight centrifugal fan.

System Design

Building specications

•

Total oor space 327,000 ft2 (30,350 m2)

Basement : Employee cafeteria

•

Ground oor : Lobby, conference room

•

2nd to 7th oor : Offices, salons, board room

•

Air conditioning system

•

Ventilation : Ceiling embedded-type Lossnay, straight centrifugal fan

•

: Basement oor SRC (Slab Reinforced Concrete), seven oors above ground oor

: Package air conditioning

1.2 System Requirements

(1) Operation system that answers individual needs was required.

Free independent operation system

•

Simple control

•

(2) Effective use of oor space

(Eliminating the equipment room)

(3) Application to Building Management Laws

Effective humidication

•

Eliminating indoor dust

•

(4) Energy conservation

1.3 Details

(1) Air Conditioning

In general offices, the duct method would applied with

•

several ceiling-embedded multiple cooling heat pump packages in each zone to allow total zone operation.

Board rooms, conference rooms, and salons would air

•

conditioned with a ceiling embedded-type or cassette-type multiple cooling heat pump package.

Installation of an office system air conditioning system – The air supplied from the Lossnay unit was introduced into the intake side of the indoor unit of air conditioner, and the stale air from the room was directly removed from the inside of the ceiling.

Return grille

EA (Exhaust air)

OA (Outdoor air suction)

EA (Exhaust air)

OA (Outdoor air suction)

SA (Supply air)

Supply grille

Indoor unit of air conditioner

SA (Supply air to room)

RA (Return air)

Grille

Indoor unit of air conditioner

Inspection

space

Lossnay

Suspension bolt position

Suspension bolt

Lossnay

Inspection hole

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Page 70

CHAPTER 6 • Examples of Lossnay Applications

(2) Ventilation

For general offices, a ceiling embedded-type Lossnay unit would be installed. The inside of the ceiling would be used as a

•

return chamber for exhaust, and the air from the Lossnay unit would be supplied to the air-conditioning return duct and mixed with the air in the air conditioning passage. (Exhaust air was taken in from the entire area, and supply air was introduced into the indoor units of air conditioner to increase the effectiveness of the ventilation for large rooms.)

For board rooms, conference rooms, and salons, a ceiling embedded-type Lossnay unit would be installed. The stale air

•

would be exhausted from the discharge grille installed in the center of the ceiling. The supply air would be discharged into the ceiling, where, after mixing with the return air from the air conditioner, it was supplied to the air conditioner.

The air in the toilet, kitchenette, and elevator hall, etc., would be exhausted with a straight centrifugal fan. The OA

•

supply would use the air supplied from the Lossnay unit. (The OA volume would be obtained by setting the Lossnay supply fan in the general office to the extra-high mode.)

Installation of air conditioning system for board rooms, conference rooms, salons - the air supplied from the Lossnay unit was blown into the ceiling, and the stale air was removed from the discharge grille.

SA (Supply air)

Discharge grille

SA (Supply air)

Discharge grille

RA (Return air)

Inspection

space

Lossnay

Suspension bolt position

Suspension bolt

Lossnay

Inspection hole

Suspension bolt position

EA (Exhaust air)

OA (Outdoor air suction)

EA (Exhaust air)

OA (Outdoor air suction)

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CHAPTER 6 • Examples of Lossnay Applications

A gallery for the exhaust air outlets would be constructed on the outside wall to allow for blending in with the exterior.

•

Reference oor indoor units of air conditioner system layout = Lossnay Air-cooling heat pump air conditioner Air-cooling heat pump air conditioner

Additional room

Women's dressing room

Office

Office machine room

Men's dressing room

Kitchenette

Machine room

Kitchenette

Men's dressing room

Office machine room

Women's dressing room

Additional rooms

Machine room

Additional rooms

Office

Additional room

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Page 72

CHAPTER 6 • Examples of Lossnay Applications

(3) Humidication

If the load uctuation of the required humidication amount was proportional to the ventilation volume, it was ideal to add a humidifier with the ventilation system. For this application, the humidifier was installed on with the air supply side of the Lossnay unit.

(4) Conforming to Building Laws

Many laws pertaining the building environments were concerned with humidication and dust removal; in these terms, it was recommended that a humidier was added to the air conditioning system to allow adequate humidication. Installing of a lter on each air-circulation system in the room was effective for dust removal, but if the outdoor air inlet was near a source of dust, such as a road, a lter should also be installed on the ventilation system.

1.4 Outcome

(1) Air conditioning and ventilation needs were met on an individual room or were basis.

(2) Operation was possible with a 24-hour system.

(3) Operation was simple because the switches were accessible in the room. (A controller was not required.)

(4) Floor space was saved.

(5) Energy was conserved with the independent energy recovery function.

(6) Air-conditioning with ventilation was possible with the independent system.

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Page 73

CHAPTER 6 • Examples of Lossnay Applications

2. Small-Scale Urban Building

2.1 System Design Challenges

The system was designed effectively using limited available air conditioner and ventilator installation space. For this application, air ow must be considered for the entire oor and the ventilator was installed in the ceiling plenum.

System Design

Application : Office

•

Building specication : RC (Reinforced Concrete)

•

Total oor space : 5,950 ft2 (552 m2) (B1 to 6F)

•

Application per oor : B1: Parking area

•

GF to 6F: Office

Air conditioning system

•

Ventilation : Ceiling-embedded-type and cassette-type Lossnay, straight centrifugal fan, duct ventilation fan.

•

2.2 System Requirements

(1) Three sides of the building were surrounded by other

buildings, and windows could not be installed; therefore mechanical ventilation needed to be reliable.

(2) Ample fresh outdoor air could not be supplied.

(3) If the exhaust in the room was large, odors from other areas

could have affected air quality.

(4) Humidication during winter was not possible.

: Package air conditioner

GF Layout 2F to 6F Layout

PAC : Package air conditioner LS : Lossnay

2.3 Details

(1) Air conditioning

Space efficiency and comfort during cooling/heating was improved with ceiling-embedded cassette-type package air

•

conditioner.

(2) Ventilation

Room Entire area was ventilated by installing several ceiling-embedded-type Lossnay units.

•

Salon Humidication was possible by adding a humidier.

•

Conference room Area was independently ventilated by installing a ceiling-embedded-type or cassette-type

•

Board room Lossnay in each room.

•

Toilet, powder room

•

Kitchenette

•

Location of air intake/exhaust air outlets on outside wall

•

The freshness of the outdoor air taken in by the Lossnay was important, and because

other buildings, the intake and exhaust ports must be placed as far apart as possible.

}

(Outdoor air was supplied to the toilet and kitchenette by setting the selection switch on the Lossnay unit for supply to the extra-high.)

} }

Area was exhausted with a straight centrifugal fan or duct ventilation fan.

(An adequate exhaust volume was obtained by introducing outdoor air into the space with the toilet being ventilated constantly.)

the building was surrounded by

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Page 74

CHAPTER 6 • Examples of Lossnay Applications

2.4 Outcome

(1) Appropriate ventilation was possible with forced simultaneous air intake/exhaust using Lossnay units.

(2) Outdoor air to the toilet and kitchenette was possible with Lossnay units, and appropriate ventilation was possible even in

highly sealed buildings.

(3) Odors inltrating into other rooms was prevented with constant ventilation using an adequate ventilation air volume.

(4) Humidication was possible by adding a simple humidifying unit to the Lossnay unit.

3. Hospitals

3.1 System Design Challenges

Ventilating a hospitals required adequate exhaust air from the generation site and ensuring a supply of ample fresh outdoor air. An appropriate system was an independent ventilation system with forced simultaneous air intake/exhaust. The fan coil and package air conditioning were according to material and place, and the air conditioned room was ventilated with ceiling-embedded-type Lossnay units. The toilet and kitchenette, etc., were ventilated with a straight centrifugal fan.

System Design

Building specication

•

Total oor space : 10,000 ft2 (931 m2) (GF to 3F)

•

Application per oor : GF : Waiting room, diagnosis rooms, surgery theater, director room, kitchen

•

2F : Patient rooms, nurse station, rehabilitation room, cafeteria 3F : Patient rooms, nurse station, head nurse room, office

Air conditioning system

•

Ventilation : Ceiling-embedded-type Lossnay, straight centrifugal fan

•

: RC (Reinforced Concrete)

: Fan coil unit, package air conditioner

3.2 System Requirements

(1) Prevented in-hospital disease transmission.

(Meeting needs for operating rooms, diagnosis rooms, waiting rooms and patient rooms were required.)

(2) Adequate ventilation for places where odors were generated

(Preventing odors generated from toilets from inltrating into other rooms was required.)

(3) Blocking external sound

(Blocking sound from outside of the building and from adjacent rooms and hallway was required.)

(4) Assuring adequate humidity

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CHAPTER 6 • Examples of Lossnay Applications

3.3 Details

(1) Air Conditioning

Centralized heat-source control using a fan coil for the

•

general system allowed efficient operation timer control and energy conservation.

A 24-hour system using a package air conditioner for

•

special rooms (surgery theater, nurse station, special patient rooms, waiting room) was the most practical.

(2) Ventilation

Hallway

•

Independent system using centralized control with large air volume Lossnay units, or independent system with ceiling suspended-type Lossnay units.

Surgery theater

•

Combination of larger air volume Lossnay and package airconditioner with HEPA lter on room supply air outlet.

Diagnosis rooms and examination room

•

Patient rooms Nurse stations Independent ventilation for each room using ceiling suspended/embedded-type Lossnay.

Integral system with optional humidifier for required

•

rooms.

Positive/negative pressure adjustment, etc., was possible

•

by setting main unit selection switch to extra-high mode (smaller air volume models) according to the room.

Toilet/kitchenette

•

Straight centrifugal fan or duct ventilation fan

Storage/linen closet

•

Positive pressure ventilation fan or duct ventilation fan. The outdoor air was supplied from the hallway ceiling with the straight centrifugal fan, and was distributed near the indoor unit of air conditioner after the air ow was reduced.

Kitchen

•

Exhaust with negative pressure ventilation fan or straight centrifugal fan. Outdoor air was supplied with the straight centrifugal fan.

Machine room

•

Exhaust with positive pressure ventilation fan.

GF Layout

Machine room

Prep room

Surgery theater

Director room

2F Layout

Kitchenette

Rehabilitation

room

Lossnay

3F Layout

Storage/ machine

room

Head nurse

Office

room

Kitchen

Inspection room

Nurse beds

Conference

Nurse beds

Nurse

station

(4 beds)

room

Nurse station

Patient

room

Medicine supply storage

Treatment room

Lossnay

Patient

room

(1 bed)

Gastro camera room

Diagnosis room

Patient

room

(1 bed)

Patient

room

(4 beds)

Patient

room

(1 bed)

Patient

room

(1 bed)

Pharmacy

Patient

room

(1 bed)

Patient

room

(1 bed)

Patient

room

(1 bed)

X-ray room

Reception

Patient

room

(1 bed)

Patient

room

(4 beds)

Patient

room

(1 bed)

Waiting room

Patient

room

(2 beds)

Storage

Cafeteria/

lounge

Lossnay

Patient

room

(1 bed)

Foyer

Storage

Patient

room

(1 bed)

Storage

3.4 Outcome

(1) The following outcomes were possible by independently ventilating the air-conditioned rooms with Lossnay units:

Disease transmission could be prevented by shielding the air between rooms.

•

Lossnay Core’s sound reducing properties reduced outside sound.

•

Because outdoor air did not need to be taken in from the hallway, doors could be sealed, shutting out sounds from the

•

hallway.

Humidication was possible by adding a humidier.

•

(2) By exhausting the toilet, etc., and supplying outdoor air to the hallway:

Odors inltrating into other rooms were prevented.

•

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Page 76

CHAPTER 6 • Examples of Lossnay Applications

4. Schools

4.1 System Design Challenges

A comfortable classroom environment was necessary to improve the students’ desires to study. Schools near airports, railroads and highways had sealed structures to soundproof the building, and thus air conditioning and ventilation facilities were required. Schools in polluted areas such as industrial districts also required air conditioning and ventilation facilities. At university facilities which had a centralized design to efficiently use land and to improve the building functions, the room environment had to also be maintained with air conditioning.

System Design

Total oor space : 247,600 ft2 (23,000 m2)

•

Building specications

•

Memorial hall wing Library wing Main management wing

4.2 System Requirements and Challenges

(1) Mainly single duct methods, fan coil unit methods, or package methods were used for cooling/heating, but the diffusion

rate was still low, and water-based heaters were still the main heating source.

(2) The single duct method was difficult to control according to the usage, and there were problems in operation costs.

(3) Rooms were often ventilated by opening windows or using a ventilation gallery; although the methods provide ample

ventilation volume, those may introduce sound coming from the outside.

: Prep school (high school wing)

4.3 Details

(1) To achieve the goals of overall comfort, saving space and

energy, an air conditioning and ventilation system with a ceiling-embedded-type fan coil unit and ceiling-embeddedtype Lossnay was installed.

(2) Automatic operation using a weekly program timer was used,

operating when the general classrooms and special classrooms were used.

(3) By using a ventilation system with a total energy recovery unit,

energy was saved and soundproong was realised.

4.4

Criteria for installing air conditioning

Classroom Layout

(Hallway) SA RA

(Classroom)

SA SA

system in schools (Example)

(1) Zoning according to application must be possible.

(2) Response to load uctuations must be swift.

(3) Ventilation properties must be ideal.

(4) The system must be safe and rmly installed.

(5) Future facility expansion must be easy.

(6) Installation in existing buildings must be possible.

(7) Installation and maintenance costs must be low.

LS LS

OA EA OA

SASA

(Veranda)

4.5 System Trends

(1) It was believed that environmental needs at schools would continue to progress, and factors such as comfort level,

ventilation, temperature/humidity, sound proong, natural lighting, and color must be considered during the design stage.

(2)

Independent heating using a centralized control method was mainly applied when the air conditioner unit was installed for heating only application. For cooling/heating, a combination of a fan coil method and package-type was the main method used.

(3) The total energy recovery unit was mainly used in consideration of the energy saved during air conditioning and the high

soundproong properties.

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CHAPTER 6 • Examples of Lossnay Applications

5. Convention Halls, Wedding Halls in Hotels

5.1 System Design Challenges

Hotels often included conference, wedding, and banquet halls. Air conditioning systems in these spaces had to have a ventilation treatment system that could handle extremely large uctuations in loads, any generated tobacco smoke, and odor removal.

5.2 Systems Requirements

The presence of CO and CO2 at permissible values, odor removal, and generated tobacco smoke were often considered in ventilation standards; often the limit was set at 18 CFM·person to 21 CFM·person (30 m3/h·person to 35 m3/h·person). Several package air conditioners with ventilation or air-handling unit facilities were often used, but these were greatly affected by differences in capacity, ratio of smokers, and length of occupancy in the area.

5.3 Details

The proposed plan had two examples using a Lossnay unit as a ventilator for total energy recovery in the air-conditioned conference room, and using several package air-conditioners with ventilation for convention and banquet halls.

A) Conference room

Energy recovery ventilation was executed with continuous operation of the Lossnay unit, but when the number of persons increased and the CO2 concentration reached a set level (for example, 1,000 ppm in the Building Management Law), a separate centrifugal fan turned on automatically. The system could also be operated manually to rapidly remove smoke and odors.

B) Convention and banquet halls

The system included several outdoor air introduction-type package air conditioners and straight centrifugal fans for ventilation. However, an inverter controller was connected to the centrifugal fan so that it constantly operated at 50 percent, to handle uctuations in ventilation loads. By interlocking with several package air-conditioners, detailed handling of following up the air condition loads in addition to the ventilation volume was possible. Systems using Lossnay were also possible.

LS : Lossnay EX : Centrifugal fan PAC : Package air conditioner

Conference Room Ventilation System Diagram

5.4 System Trends

The load characteristics at hotels was complex compared to general buildings, and were greatly affected by the occupancy, and operation. Because of the high ceilings in meeting rooms and banquet halls preheating and precooling also needs to be considered. Further research on management and control systems and product development would be required to achieve even more comfortable control within these spaces.

U-68

EX : Centrifugal fan PAC : Package air conditioner IB : Inverter controller

Convention and Banquet Hall Ventilation System Diagram

Page 78

CHAPTER 6 • Examples of Lossnay Applications

Public Halls (Facilities Such as Day-care Centers)

6.1 System Design Challenges

For buildings located near airports and military bases, etc., that required soundproofing, air conditioning and ventilation facilities had conventionally been of the centralized type. However, independent dispersed air conditioning and ventilation systems had been necessary due to the need for zone control, as well as for energy conservation purposes. The system detailed below was a plan for these types of buildings.

System Design

Building specications

•

Application : GF Study rooms (two rooms), office, day-care room, lounge

•

Air conditioning : GF Air-cooling heat pump chiller and fan coil unit

•

Ventilation : Ceiling-embedded Lossnay unit

•

: Two oors above ground oor, Total oor space: 4,150 ft2 (385 m2)

.....

Meeting room

.....

Air-cooling heat pump package air conditioner

6.2 System Requirements

(1)

Conventional systems used centralized units with air-handling units, and air conditioning and ventilation were performed together.

(2) Topics

1) Special knowledge was required for operation, and there were problems in response to the users’ needs.

2) When the centralized method was used, the air even in rooms that were not being used was conditioned, increasing operation costs.

3) Machine room space was necessary.

4) Duct space was necessary.

6.3 Details

(1) Air-conditioning Facilities

1) Small rooms : Air-cooling heat pump chiller and fan coil unit combination

2) Meeting rooms : Single duct method with air-cooling heat pump package air conditioner

(2) Ventilation Facilities

1) A ceiling-embedded-type Lossnay unit was used in each room, and a silence chamber, silence-type supply/return grille, silence duct, etc. was incorporated on the outer wall to increase the total soundproong effect.

6.4 Outcome

(1) Operation was possible without special training, so system management was easy. (2) Zone operation was possible, and was thus energy-saving. (3) Soundproof ventilation was possible with the separately installed ventilators. (4) Energy saving ventilation was possible with the energy recovery ventilation. (5) Ceiling-embedded-type Lossnay unit saved space.

Ground Floor Layout 2F Layout

Machine room

PAC

Kitchenette

Stairway

Study room

FCU

Toilet

Hall

FCU

Day-care room

PAC

Meeting room

Lounge

Foyer

Study room

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Page 79

Page 80

CHAPTER 7

Installation Considerations

Page 81

CHAPTER 7 • Installation Considerations

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

LGH- F300 · F470 · F600RX5

Installation diagram

Always leave inspection holes ( 18 or 24) on the air

•

lter and Lossnay Core removal side.

Always insulate the two ducts outside the room (intake

•

air and exhaust air ducts) to prevent condensation.

It is possible to change the direction of the outside air

•

ducts (OA and EA side).

Do not install the vent cap or round hood where it will

•

come into direct contact with rain water.

Air volume (CFM) Model

300

470

600

LGH-F300RX type

LGH-F470RX type

LGH-F600RX type

(Exhaust air)

(Outside air)

Duct downward slope 1/30 or more (to wall side)

(Rainwater entrance prevention)

Deep hood or weather cover

EA (Exhaust air)

OA (Outside air)

5 7/8 to 9 7/8

23 5/8 or more

Duct diameter 8”dia (ordered by customer)

Suspension bolt position (ordered by customer)

Suspension bolt position

Inspection

opening

Inspection opening

Exhaust air grille

Lossnay Core/ air filter/ fan maintenance space

(Return air)

Suspension bolt position

16 5/16

Suspension bolt position

Supply air grille

16 5/16

Supply/ exhaust air grille

SA (Supply air)

Unit (inch)

Dimension

A B

34 1/2 41 7/8

39 3/4

40 13/16

39 3/4 49 3/4

LGH- F1200RX5

Installation diagram

Ceiling Exhaust grille (user supplied)

(exhaust-air outlet)

Air-supply grille (user supplied)

(fresh-air intake)

Duct (user supplied)

Duct incline Over 1/30 (toward the wall)

to prevent entry of rainwater

(exhaust-air outlet)

(fresh-air intake)

suspension

bolt position

50 1/8

(user

supplied)

18( 24) Inspection port

Duct diameter 10”dia (user supplied)

39 3/4

18( 24)

Inspection port

Heat exchanger/filter maintenance space

Ceiling suspension bolt

(user supplied)

Exhaust grille (user supplied)

Y piping,Dwindle pipe

(user supplied)

Min. 23 5/8

5 7/8 to 9 7/8

Ceiling suspension bolt position

(return air)

Exhaust grille

(return air)

Air-supply grille

(user supplied)

Air-supply grille (user supplied)

Air-supply grille

(supply air)

Ceiling suspension

bolt position

Duct diameter 8”dia

(user supplied)

Always leave inspection holes ( 18 or 24) on the air

•

lter and Lossnay Core removal side.

Always insulate the two ducts outside the room (intake

•

air and exhaust air ducts) to prevent condensation.

If necessary, order a weather cover to prevent rain water

•

from direct contact or entering the unit.

Ducting Indoor Outdoor

Heating-insulation material

Taping

Duct

Duct connecting flange

Should secure with airtight tape to prevent air leakage.

Heating-insulation material

Taping

Should secure with airtight tape to prevent air leakage. Cover duct with insulation foam prevent condensation.

EA (exhaust air outlet)

OA (outside air intake)

Electrically operated damper (Protection against the intrusion of cold air

while Lossnay is stopped in winter)

(To be provided by the customer)

EA (exhaust air outlet)

OA (outside air intake)

U-72

Lossnay unit

Unit (inch)

In a region where there is risk of freezing in winter, it is

•

recommended to install an Electrically operated damper, or the like, in order to prevent the intrusion of (cold) outdoor air while Lossnay is stopped.

Page 82

CHAPTER 7 • Installation Considerations

1.1 Choosing the Duct Attachment

Choose between two directions for the outside duct (OA, EA) piping direction for alternative installation.

Standard Installation Alternative Installation

*A space is

necessary to prevent rain water from entering the unit.

It is possible

to set the unit close to a wall.

To avoid obstructing

the supply and exhaust ducts.

Lights, etc.

1.2 Installation and Maintenance

(1) Always leave an inspection hole ( 18) to access the lter and Lossnay Core.

(2) Always insulate the two ducts outside the room (intake air and exhaust air ducts) to prevent frost from forming.

(3) Prevent rainwater from entering.

Apply a slope of 1/30 or more towards the wall to the intake air and exhaust air ducts outside the room.

•

Do not install the vent cap or round hood where it will come into direct contact with rainwater.

•

(4) Use the optional “control switch” (Ex. PZ-60DR-E, etc.) for the RX5-type.

A MELANS centralized controller can also be used.

1.3 Installation Applications

(1) Installing Two Units to One Outside Air Duct

The main unit’s supply outlet and suction inlet and the room side and outdoor side positions cannot be changed. However, the unit can be installed upsidedown, and installed as shown below. (This is applicable when installing two units in one classroom, etc.)

Reversed installation

RA RA

Lossnay Lossnay

OA EA

Inspection

opening

SA SA

Standard installation

(2) System Operation with Indoor Unit of Air Conditioner

There is an increased use of air conditioning systems with independent multiple air-conditioner unit due to their features such as improved controllability, energy conservation and saving space. For these types of air conditioning systems, combining the operation of the dispersed air conditioners to Lossnay is possible.

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

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

Return grille

Ceiling embeddedtype Lossnay unit

Exhaust Air intake

Ceiling

Ceiling embeddedtype Lossnay unit

Exhaust Air intake

Ceiling

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Page 83

Page 84

CHAPTER 8

Filters

Page 85

CHAPTER 8 • Filters

1. Importance of Filters

Clean air is necessary for comfort and health. Besides atmospheric pollution that has been generated with the development of modern industries, the increased use of automobiles, air pollution in air-tight room has progressed to the point where it has an adverse effect on occupants. Also, demands for preventing pollen from entering inside spaces are increasing.

2. 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 lters

Table 2. Dust Concentrations

Type Reference Data

Outdoor air dust concentration

Indoor dust concentration

Solid particles

Fluid particles

Major particles

Aerosol particle

Air lters

3.94×10-53.94×10

Viruses

HEPA lter

Aerosol particle diameter (mil)

-4

Fumes Dust

Tobacco smoke

Carbon black

ZnO fumes

1. 2 ×10

-3

3.94×10

Mist

Clay

Oil fumes

Sea salt particles

Atmospheric

dust

-2

3.9×10-23.9×10

Bacteria

Medium to high efficiency lters

-1

Mud Sand

Fry ashes

Coal dust

Cement

Pollen

Hair

Fine dust, coarse dust llers

393.9

Sprays

Large city 6.24 - 9.36 × 10-9 (lb/ft3) 0.1 - 0.15 mg/m

Small city 6.24 × 10-9 (lb/ft3) 0.1 mg/m3 or less

Industrial districts 1.25 × 10-9 (lb/ft3) 0.2 mg/m3 or more

General office 3.5 × 10-4 (ounce/h) 10 mg/h per person

Stores 0.00018 (ounce/h) 5 mg/h per person

Applications with no tobacco smoke 0.00018 (ounce/h) 5 mg/h per person

Remarks:

1. Outdoor dust is said to have a diameter of 0.08 mil (2.1 µm); the 11 types of dust (average diameter 0.08 mil (2.0 µm)) as listed by JIS Z8901 for performance test particles are employed.

2. Dust in office rooms is largely generated by cigarette smoke, and its diameter is 0.028 mil (0.72 µm). The 14 types of dust (average 0.031 mil (0.8 µm)) as listed by JIS Z 8901 for performance test particles are employed.

3. Dust generated in rooms where there is no smoking has approximately the same diameter as outdoor air.

4. Smoking in general offices (Japan):

Percentage of smokers : Approx. 70% (adult men) Average number of cigarettes : Approx. 1/person·h (including non-smokers)

Length of cigarette

(tobacco section)

: Approx. 1.6 inch (4 cm)

Amount of dust generated by one cigarette : Approx. 3.5 × 10-4 ounce/cigarette (10 mg/cigarette)

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Page 86

CHAPTER 8 • Filters

100

Calculation Table for Dust Collection Efficiency of Each Lossnay Filter

Tested

Filter type

Pre-lter NP/400

Measurement

method

dust

Applicable

model

Commercial Lossnay

(LGH)

AFI

Gravitational

method

Compound

dust

82% 8% - 12% Protection of heat recovery element

ASHRAE

Colorimetric

method

Atomspheric

dust

Application

3.1 Pressure Loss

Effectiveness of the filters used in the Lossnay units are shown below, expressed in terms of collection ratio (%).

Colourimetric method 90% lter

Collection ratio (%)

7. 9 ×10-31. 2 ×10-21. 6 ×10-22.4×10

-2

3.1×10

3.9×10

-2

NP/400

-2

7. 9 ×10-21. 1 ×10-11. 6 ×10-12.4×10

Particle diameter (mil)

-1

3.1×10

3.9×10

-1

7. 9 ×10-11. 2 1. 6 2.4 3.1 3.9

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Page 87

CHAPTER 8 • Filters

4. Comparing Dust Collection Efficiency Measurement

Methods

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

Test Method Test Dust

AFI Gravitational method

NBS Colorimetric method

DOP Counting method

ASHRAE Gravitational method

ASHRAE Colorimetric method

Air lter test for air conditioning set by Japan Air Cleaning Assoc. (Colorimetric test)

Pre-lter test set by Japan Air Cleaning Assoc. (Gravitational test)

Electrostatic air cleaning device test set by Japan Air Cleaning Assoc. (Colorimetric test)

Synthetic:

• Dust on standard

road in Arizona: 72%

•

K-1 carbon black: 25%

• No. 7 cotton lint: 3%

Atmospheric dust

Diameter of dioctylphthalate small drop particles: 0.01mil (0.3 µm)

Synthetic:

•

Regulated air cleaner

ne particles: 72%

•

Morocco Black: 23%

• Cotton linter: 5%

Atmospheric dust

JIS 11-type dust

JIS 8-type dust

JIS 11-type dust

Inward Flow Dust

Measurement Method

Dust weight measured beforehand

Degree of contamination of white lter paper

Electrical counting measurement using light aimed at DOP

Dust weight measured beforehand

Degree of contamination of white lter paper

Dust weight measured beforehand.

Degree of contamination of white lter paper

Outward Flow Dust

Measurement Method

• Filter passage air

volume measured

• Weigh the dust

remaining on the lter and compare

Degree of contamination of white lter paper

Same as left Counting ratio

• Filter passage air

volume measured

• Weigh the dust

remaining on the lter and compare

Degree of contamination of white lter paper

• Filter passage air

volume measured

• Weigh the dust

remaining on the lter and compare.

Degree of contamination of white lter paper

Efficiency

Indication Method

Gravitational ratio Synthetic dust lters

Comparison of contamination of reduction in degree of contamination

Gravitational ratio

Comparison of percentage of reduction in degree of contamination

Gravitational ratio Pre-lter

Comparison of percentage of reduction in degree of contamination

Type of Applicable

Filters

Electrostatic dust percentage of (for air conditioning)

Absolute lter and same type of high efficiency lter

Pre-lter Filter for air conditioning (for coarse dust)

Filter for air conditioning (for ne dust) Electrostatic dust collector

Filter for air conditioning

Electrostatic dust collector

U-78

Page 88

CHAPTER 8 • Filters

Gravitational Method

This method is used for air filters that remove coarse dust (0.39 mil (10 µm) or more). The measurement method is determined by the gravitational ratio of the dust amount on the in-flow and out-flow sides.

Dust collection ratio =

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

In-flow side dust amount

Orice

Window

Specimen

Dust supply device

Manometer

Motor

100 (%)

Dust container

Mixing blades

Dust collection lter

Performance test device Example of dust supply device

Rectifying grid

Air volume adjustment plate

Air-feed fan

Dust supply outlet

Colorimetric Method

The in-flow side air and out-flow side air are sampled using 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 =

Air-feed fan

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

Out-flow side sampling amount

Coupling pipe

Coupling

Square duct

Orice

Rectifying grid

Round duct

3.5D3D 2D 2L 2L

pipe

Pressure loss concentration measurement position

Specimen

Rectifying grid

Baffle plate

Coupling pipe

7.9(200)

7° or less

10.5R

(267R)

Venturi pipe

3.9R

(100R)

100 (%)

Dust chamber

Air lter

21.7(500)

Throttle device

Unit (inch(mm))

U-79

Page 89

CHAPTER 8 • Filters

5. Calculating Dust Concentration Levels

An air conditioning system using Lossnay units is shown below. Dust concentration levels can be easily determined using this diagram.

Dust Concentration Study Diagram

Indoor unit of air conditioner

Indoor unit lter ηi

Co :

Outdoor air dust concentration (Ib/ft3 (mg/m3)) Ci : Indoor dust concentration (Ib/ft3 (mg/m3)) G :

Amount of dust generated indoors (Ib/h (mg/h))

Qo :

Outdoor air intake amount (CFM (m3/h))

Qi :

Indoor unit of air conditioner air volume (Total air volume of indoor unit) (CFM (m3/h))

Lossnay unit

High-efficiency lter ηo

ηo : Filtering efficiency of humidier with high efficiency lter %

(colorimetric method)

ηi : Efficiency of the lter for the indoor unit of air conditioner %

(colorimetric method)

When the performance of each machine is known, the indoor dust concentration Ci may be obtained with the filter performance,

and

Also, with the value of Ci and

having been set to specific values as per manufacturer's data. The following formula is used:

Ci Q

) – Ci Q

)

known, indoor unit of air conditioner efficiency can be found using:

× 100

G + Co Qo (1 –

Ci =

G + Co Qo (1 –

Qo + Qi

U-80

Page 90

CHAPTER 9

Service Life and Maintenance

Page 91

CHAPTER 9 • Service Life and Maintenance

2.1 Removing the parts

1. Service Life

The Lossnay Core has no moving parts, which eliminates vibration problems and permits greater installation flexibility. In addition, chemicals are not used in the energy recovery system. Performance characteristics remain constant throughout the period of service. A lifetime test, currently in progress and approaching thus for 17,300 hours, has revealed no evidence of either reduction in energy recovery efficiency or material deterioration. If 2,500 hours is assumed to be the number of hours an air conditioner is used during a year, 17,300 hours equals to about seven (7) years. (This is not a guarantee of the service life.)

2. Cleaning the Lossnay Core and Pre-lter

Remove all dust and dirt on air filters and Lossnay cores at regular intervals in order to prevent a deterioration in the Lossnay functions. Guideline: Clean the air filters once a year. (or when “FILTER” and “CLEANING” are indicated on the remote controller) Clean the Lossnay cores once two year. (Clean the Lossnay cores once a year If possible.) (Frequency should be increased depending on the extent of dirt.)

1) Maintenance cover

Locate and remove the cover fixing screw. Pull back the hinged clip. Open the door and lift off of the hinge brackets.

2) Lossnay cores

Take hold of the handle and draw the Lossnay cores out from the main unit.

Models LGH-F300 to F600RX Models LGH-F1200RX5:

3) Air filters

After pulling out the Lossnay cores, undo filter guides, then remove the air filters, located at the bottom left and right of the Lossnay cores, as below.

5: 2 cores

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

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

4 cores

Maintenance cover

Hinge

Hinge bracket

Models LGH-F300 to F600RX5 Models LGH-F1200RX5

Handle

Models LGH-F300 to F600RX

Lossnay core

Main unit

Air filter

5 Models LGH-F1200RX5

Filter stopper

Hinge

Handle

Lossnay core

Maintenance cover

Main unit

Air filter

Hinge bracket

Models LGH-F300 to F600RX Models LGH-F1200RX

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

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

CAUTION

Bow filter stoppers a little to remove them from filter guide.

Take filter stoppers careful not to break them.

U-82

4 filters 8 filters

Filter guide

Page 92

2.2 Cleaning the parts

1) Air filters

Use a vacuum cleaner to remove light dust. To remove stubborn dirt wash in a mild solution of detergent and lukewarm water. (under 104 F (40 C))

CAUTION

Never wash the filters in very hot water and never wash them by rubbing them.

Do not dry the filters by exposing them to a flame.

2) Lossnay cores

Use a vacuum cleaner to suck up the dust and dirt on the exposed surfaces of the Lossnay cores. Use a soft brush only to clean exposed surface areas.

CAUTION

Do not use the hard nozzle of the vacuum cleaner. It may damage the exposed surfaces of the Lossnay cores.

Under no circumstances should the Lossnay cores be washed in water.

CHAPTER 9 • Service Life and Maintenance

Vacuum cleaner

Air filter

Do NOT wash in water.

Vacuum cleaner (with brushi attachment)

Lossnay core

Corner

2.3 Assembly after maintenance

Bearing in mind the following points, assemble the parts following the sequence for their removal in reverse.

Arrange the Lossnay core with the air filter side as shown in the name plate on the Lossnay unit.

Note

If “FILTER” and “CLEANING” are indicated on the remote controller, turn off the indication, after maintenance.

U-83

Page 93

Page 94

CHAPTER 10

Ventilation Standards in Each Country

Page 95

CHAPTER 10 • Ventilation Standards in Each Country

1. Ventilation Standards in Each Country

1.1 Japan

Summary of Laws Related to Ventilation

Related Laws

Law for Maintenance of Sanitation in Buildings

The Building Standard Law of Japan

Item

Acceptable Range Room Environment Standard Values Remarks

Buildings of at least 3,000 m2 (for schools, at least 8,000 m2).

Buildings with requirements for ventilation equipment.

1) Windowless rooms.

2) Rooms in theaters, movie theaters, assembly halls, etc.

3) Kitchens, bathrooms, etc.

Rooms with equipment or devices using re.

If a central air quality management system or mechanical ventilation equipment is installed, comply with the standard target values shown in the table below.

Impurity Volume of

Particles

CO Rate

CO2 Rate Less than 1,000 ppm.

Temperature

Relative Humidity 40% - 70%

Ventilation Less than 0.5 m/sec.

Central air quality management system ventilation capacity and characteristics

Effective ventilation capacity V 20Af/N(m3) Af: Floor space (m2); N: Floor space occupied by one person

Impurity Volume of

Particles

CO Rate Less than 10 ppm.

2 Rate Less than 1,000 ppm.

Temperature

Relative Humidity 40% - 70%

Ventilation Less than 0.5 m/sec.

Less than 0.15 mg per 1 m3 of air

Less than 10 ppm. (Less than 20 ppm when outside supply air has a CO rate of more than 10 ppm.)

1) Between 17°C and 28°C When making the room

temperature cooler than the outside temperature, do not make the difference too great.

Less than 0.15 mg per 1 m3 of air

1) Between 17°C and 28°C When making the room

temperature cooler than the outside temperature, do not make the difference too great.

Applicable buildings are those designed to serve a specic purpose.

Applicable buildings are those with ventilation equipment requirements.

Industrial Safety and Health Act

Offices. (Office sanitation regulated standards)

U-86

For general ventilation, the effective ventilation area opening is at least 1/20 of the oor space, and the ventilation equipment installed gives a CO density of 50 ppm and CO2 density of 5,000 ppm or less. If a central air quality management system or mechanical ventilation equipment is installed, comply with the standard target values shown in the table below.

Impurity Volume of

Particles

CO Rate

CO2 Rate Less than 1,000 ppm.

Air Flow

Heat and Humidity

Conditions

Air (1 atmospheric pressure, 25°C) less than 0.15 mg per 1 m

Less than 10 ppm. (Less than 20 ppm when outside supply air has a CO rate of more than 10 ppm.)

Air ow in room is less than

0.5 m/s, and air taken into the room

does not blow directly on or reach occupants.

Heat between 17°C - 28°C Relative humidity 40% - 70%

of air

Page 96

CHAPTER 10 • Ventilation Standards in Each Country

2. United States of America

ASHRAE Standard 62 - 2010 Table 6-1 Minimum ventilation rate in breathing zone

People Outdoor

Occupancy

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

Specifications and Main Features

Frequently Asked Questions

User Manual