Mitsubishi LGH-15RX5-E, LGH-35RX5-E, LGH-50RX5-E, LGH-80RX5-E, LGH-100RX5-E TECHNICAL MANUAL

TECHNICAL MANUAL

Models Lossnay Unit

LGH-15RX5-E
LGH-50RX

5-E

LGH-100RX

5-E

LGH-25RX

5-E

LGH-65RX

5-E

LGH-150RX

5-E

LGH-35RX

5-E

LGH-80RX

5-E

LGH-200RX

5-E

Lossnay Remote Controller

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

i

CONTENTS

Lossnay Unit

CHAPTER 1 Ventilation for Healthy Living

1. Necessity of Ventilation

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

U-2

2. Ventilation Standards

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

U-4

3. Ventilation Method

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

U-5

4. Ventilation Performance

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

U-8

5. Ventilation Load

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

U-10

CHAPTER 2 Lossnay Construction and Technology

1. Construction and Features

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

U-16

2. Lossnay Core Construction and Technology

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

U-16

3. Total Energy Recovery Efficiency Calculation

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

U-18

4. What is a Psychrometric Chart?

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

U-19

5. Lossnay Energy Recovery Calculation

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

U-20

CHAPTER 3 General Technical Considerations

1. Lossnay Energy Recovery Effect

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

U-22

2. Calculating Lossnay Cost Savings

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

U-24

3. Psychrometric Chart

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

U-26

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

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

U-27

5. Lossnay Core Fire : retardant property

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

U-29

6. Lossnay Core Sound Reducing Properties Test

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

U-30

7. Changes in the Lossnay Core

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

U-31

8. Comparing Energy Recovery Techniques

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

U-33

CHAPTER 4 Characteristics

1. How to Read the Characteristic Curves

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

U-36

2. Calculating Static Pressure Loss

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

U-36

3. How to Obtain Efficiency from Characteristic Curves

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

U-40

4. Sound

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

U-41

5. NC Curves

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

U-47

CHAPTER 5 System Design Recommendations

1. Lossnay Operating Environment

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

U-52

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

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

U-53

3. Attaching Air Filters

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

U-53

4. Constructing the Ductwork

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

U-53

5. Bypass Ventilation

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

U-53

6. Night purge function

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

U-53

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

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

U-54

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

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

U-55

9. Automatic Ventilation Switching

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

U-56

10. Alternate Installation for Lossnay

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

U-57

11. Installing Supplementary Fan Devices

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

U-58

ii

CHAPTER 6 Examples of Lossnay Applications

1. Large Office Building

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

U-60

2. Small-Scale Urban Building

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

U-64

3. Hospitals

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

U-65

4. Schools

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

U-67

5. Convention Halls, Wedding Halls in Hotels

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

U-68

6.

Public Halls (Facilities such as Day-care Centers)

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

U-69

CHAPTER 7 Installation Considerations

1. LGH-Series Lossnay Ceiling Embedded-Type (LGH-RX

5 Series)

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

U-72

CHAPTER 8 Filters

1. Importance of Filters

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

U-76

2. Dust

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

U-76

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

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

U-77

4. Comparing Dust Collection Efficiency Measurement Methods

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

U-79

5. Calculating Dust Concentration Levels

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

U-81

6. Certificate in EU

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

U-81

CHAPTER 9 Service Life and Maintenance

1. Service Life

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

U-84

2. Cleaning the Lossnay Core and Pre-filter

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

U-84

CHAPTER 10 Ventilation Standards in Each Country

1. Ventilation Standards in Each Country

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

U-88

2. United States of America

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

U-89

3. United Kingdom

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

U-89

CHAPTER 11 Lossnay Q and A

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

U-92

iii

Lossnay Remote Controller

1. Summary

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

C-3

2. Applicable Models

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

C-3

3. Terminology

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

C-4

4. System Features and Examples

4.1 Features

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

C-5

4.2 System Examples

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

C-6

4.3 System Selection

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

C-8

4.4 Basic System

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

C-11

4.5 Interlocking with Mr. Slim

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

C-13

4.6 Combining with City Multi

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

C-14

5. Examples of Applications Using Various Input and Output Terminals

5.1 External Control Operating Mode Selection

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

C-23

5.2 Delayed Interlocked Operation

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

C-24

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

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

C-24

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

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

C-25

5.5 Operation monitor output

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

C-26

5.6 Malfunction monitor output

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

C-26

5.7 By-pass operation monitor output

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

C-26

5.8 Connection Method

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

C-26

5.9

When switching High/Low/Extra-Low fan speed externally (when CO

2

sensor or other equipment is connected)

....

C-28

5.10 When switching By-pass externally

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

C-29

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

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

C-29

5.12

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

....

C-30

6. Precautions When Designing M-NET Systems

6.1 M-NET Transmission Cable Power Supply

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

C-31

6.2

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

........

C-31

6.3 Wiring Example

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

C-32

6.4 Power Supply to the Indoor Unit Transmission Cable

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

C-33

7. M-NET Cable Installation

7.1 Precautions When Installing Wiring

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

C-34

7.2 Electrical Wiring

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

C-35

7.3 Control Cable Length

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

C-36

8. M-NET System Designs

8.1 Address Definitions

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

C-37

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

)

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

C-39

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

)

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

C-39

iV

9. Automatic Ventilation Switching

9.1 Effect of Automatic Ventilation Mode

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

C-40

9.2 Ventilation mode control

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

C-40

10. Troubleshooting

10.1 Service Flow

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

C-44

10.2 Checklist

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

C-45

11. Installation method

11.1 Electrical installation

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

C-64

11.2 Connecting the power supply cable

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

C-66

11.3 System configuration

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

C-66

11.4 Function Setting

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

C-72

11.5 Trial operation

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

C-76

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

12.1 Parts Names

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

C-78

12.2 Setting the Day of the Week and Time

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

C-79

12.3 Using the Remote Controller

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

C-79

12.4 Care and Maintenance

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

C-83

12.5 Servicing

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

C-83

12.6 How to Install

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

C-84

12.7 Test Run

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

C-85

12.8 Function Selection

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

C-86

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

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

C-91

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

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

C-92

15. Appendix

15.1 Centralized Controller (AG-150A)

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

C-93

15.2 Remote Controllers for Mr. Slim indoor units

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

C-100

15.3 ME Remote Controller (PAR-F27MEA)

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

C-103

Lossnay Unit

CHAPTER 1

Ventilation for Healthy Living

U-2

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
increasingly being 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”.
In Japan ventilation regulations are detailed in the “Building Standard Law Enforcement Ordinance” and the “Building
Management Law” for upholding a sanitary environment in buildings. These are similar to regulations in other countries.

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 3,000m

2

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)

Specific Account of Buildings in Tokyo (March, 2003)

Note: Excludes buildings with an expanded floor space of 3,000 to 5,000m

2

in particular areas.

Results of the air quality measurement public
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
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

82

83 84

85

86

87

88

899091 92 93 9495 96 97 98 9900 01 02 03 0405 06

(year)

0

10

20

30

40

50

60

relative humidity

carbon dioxide

temperature

carbon monoxide

ventilation

floating particles
(tobacco smoke)

Percentage Unsuitable Air Quality by Year

(From reference data in the 2006 edition of the “Water Supply

Division, Dept. of Localized Public Health, Tokyo Metropolitan
Government, Bureau of Public Health”)

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

U-3

CHAPTER 1 ● Ventilation for Healthy Living

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

Concentration (ppm)

Effect of Concentration Changes

0.01 - 0.2 Standard atmosphere.

5Tolerable long-term value.

10

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

20

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

50

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

100

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

200 Light headache in the 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

Level may be found in automobile exhaust.

(Several %)

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

Concentration (%) Standards and Effect of Concentration Changes

Approx. 21 Standard atmosphere.

20.5

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)

20 - 19

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

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

16 Normal concentration in exhaled air.

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

15 Flame in combustion devices will extinguish.

12 Short term threat to life.

7 Fatal

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 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 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

U-4

CHAPTER 1 ● Ventilation for Healthy Living

Effect of Carbon Dioxide (CO2)

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

1.3 Effect of Air Contamination in Buildings

●

Dirtiness of interior
New ceilings, walls and ornaments will turn yellow from dust and tobacco smoke tar 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.
In Japan, regulations are set in the “The Building Standard Law of Japan Enforcement Ordinance”, the so-called “Building
Management Law” for securing a sanitary buildings environment. According to the “Building Standards Law”, a minimum of 20

m

3

/h per occupant of ventilation air is required.

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

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

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%.

3Work and physical functions deteriorate, increase breathing doubles.

4 Normal exhalation concentration.

4 - 5

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

2 deficiency also occurs, conditions will rapidly deteriorate and become dangerous.

8

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

2 deficiency .

18 or more Fatal

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 CO

2.

U-5

CHAPTER 1 ● Ventilation for Healthy Living

3. Ventilation Method

3.1 Ventilation Class and Selection Points

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

Mechanical Ventilation Classification

Ventilation Classification (According to Building Standards Law)

1. Class 1 Ventilation

Ventilation air is mechanically
brought in and simultaneously, the
stale air in the room is mechanically
discharged.

2. Class 2 Ventilation

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

3. Class 3 Ventilation

The stale air in the room is
mechanically discharged and
simultaneously ventilation air is
mechanically introduced from the
supply air diffuser (natural).

Ex. of Application

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

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

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

• Surgery theater.

• Cleanrooms.

• Food processing
factories.

• Local ventilation in
kitchens.

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

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

• General ventilation.

System Effect

By changing the
balance of the supply
fan and exhaust fan’s
air volumes, the
pressure in the room
can be balanced,
without restrictions,
and the interrelation
with neighboring
spaces can be set
without restrictions.

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

The exhaust air is
removed from an area
in the room, and
dispersing of the stale
air can be prevented
by applying negative
pressure.

Design and

Construction Properties

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

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

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

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

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

•Effective exhausting
of dispersed stale air
is possible from an
exhaust air outlet.

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

Selection Points

• Accurate supply air
diffuser can be
maintained.

• The room pressure
balance can be
maintained.

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

• The pressure is
positive.

•

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

•

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

• The room pressure
is negative.

• Local exhaust is
possible.

•Ventilation without
dispersing stale air is
possible.

•Ventilation with
reduced air flow is
possible.

•

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

Supply
air
diffuser

Exhaust
fan

Exhaust
air
outlet

Exhaust
fan

Exhaust
fan

Stale
air

Ventilation
air

Supply Exhaust Ventilation Volume Room Pressure

Class 1 Mechanical Mechanical Random (constant) Random

Class 2 Mechanical Natural Random (constant) Positive pressure

Class 3 Natural Mechanical Random (constant) Negative pressure

Class 4 Natural Mechanical & natural Limited (inconstant) Negative pressure

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

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

3)

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

U-6

CHAPTER 1 ● Ventilation for Healthy Living

3.2 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

Air intake

(ventilation

air)

Filters

Air exhaust
(stale air)

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

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

Exhaust grill

Ceiling recessed­type Lossnay

Exhaust air
Ventilation air

Finished ceiling

Exhaust air
Ventilation air

Finished ceiling

Lossnay

Supply fan

Exhaust

Each unit

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

Ceiling recessed­type Lossnay

Exhaust grill

Exhaust air
Ventilation air

Finished ceiling

Ceiling recessed­type Lossnay

Exhaust grill

Supply grill

U-7

CHAPTER 1 ● Ventilation for Healthy Living

Comparing Centralized Ventilation and Independent Zoned Ventilation Methods

Centralized Ventilation Method

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

• Independent equipment room is required.

• Duct space is required.

• Penetration of floors with vertical shaft is not
recommended in terms of fire prevention.

Generalized per system.

• Design of outer wall is not lost.

• The indoor supply air diffuser and return grille
can be selected 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.

• 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.

Fan Power

Installation Area

Zoning

Design

Control

Comfort

Maintenance and
Management

Trouble influence

Costs

Independent Zoned Ventilation Method

As the air transfer distance is short, the fan power
is small.

• Independent equipment room is not required.

• Piping space is required only above the ceiling.

Can be used for any one area.

• The number of intakes and exhaust air outlets
on an outside wall will increase; design must be
considered.

• The design will be fixed due to installation
fittings, 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 off­peak hours.

• 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.

System FlexibilitySystem Management

U-8

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 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 Pa. units. 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 typhoon presses against a building.

4.2.3 Total Pressure

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

U-9

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 Orifice (JIS B 8628 Standards)

Static pressure (

H

)

Air volume (Q)

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).

Connection

Wind dispersing place

Connection

Smoothing

grid

Smoothing

grid

Supply

Air

(SA)

Chamber

Return

Air

(RA)

Smoothing
net

Smoothing

net

Wind gauge

duct path

Orifice

Wind gauge

duct path

Orifice

Damper

Blower

Blower

Test unit

Test unit

Static pressure in chamber
(Static pressure measurement)

Static pressure in chamber
(Static pressure measurement)

Pressure

difference before

and after orifice

(Air volume

measurement)

A) When measuring the supply air volume (with the orifice plate)

B) When measuring the return air volume (with the orifice plate)

U-10

CHAPTER 1 ● Ventilation for Healthy Living

5. Ventilation Load

5.1 How to Calculate Each Approximate Load

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)

= γ [kg/m

3

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

γ : Specific air gravity - 1.2 kg/m

3

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

occupant

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 - kJ/kg
iR : Indoor enthalpy - kJ/kg

Floor Space per Occupant (m

2

)

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

Required Ventilation Air Intake Volume Per Occupant (m

3

/h·occupant)

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.

Office Building

Department Store, Shop

Restaurant

Theater or

Average Crowded Empty

Cinema Hall

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

Application Example

Required Ventilation Volume

Amount of Cigarette Smoking

Recommended Value Minimum Value

Broker’s office

Extremely Heavy Newspaper editing room 85 51

Conference room

Quite Heavy

Bar

51 42.5

Cabaret

Heavy

Office

25.5

17

Restaurant 20

Light

Shop

25.5 17

Department store

None

Theater 25.5 17
Hospital room 34 25.5

U-11

CHAPTER 1 ● Ventilation for Healthy Living

Cooling Load Per Unit Area

When the volume of ventilation air per occupants is 25 m

3

/h, and the number of occupants per 1 m2is 0.2, the cooling load will

be approximately 157.0 W/m

2

.

● Ventilation Load

Standard design air conditions in Tokyo

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 Classifications

(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.

Typical Load Values During Cooling

Load Type Load

Ventilation Air Load

53.0 W/m

2

Indoor

Occupants 26.4 W/m

2

Generated Heat

Lighting Equipment 30.0 W/m

2

Indoor Penetration Heat 47.6 W/m

2

Total 157.0 W/m

2

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

Class Heat Load

Heat generated from walls (qWS)

(a) Indoor penetration heat

Heat generated from glass

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

Accumulated heat load in walls (q

SS)

Generated heat from occupants

Sensible heat (qHS)

(b) Indoor generated heat

Latent heat (qHL)

Generated heat from electrical equipment

Sensible heat (q

ES

)

Latent heat (q

EL)

(c) Reheating load (q

RL)

(d) Outdoor air load

Sensible heat (q

FS)

Latent heat (qFL

)

}

}

}

}

Dry Bulb Temp.

Relative Humidity

Wet Bulb Temp. Enthalpy Enthalpy Difference

Cooling

Outdoor Air 33 °C 63% 27 °C 85 kJ/kg

31.8 kJ/kg

Indoor Air 26 °C 50% 18.7 °C 53.2 kJ/kg

When the load per floor area of 1 m2with a ventilation volume of 25 m3/h·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 m

3

/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.

Ventilation air

load 33.8%

53.0 W/m

2

Indoor
penetration
heat 30.3%

47.6 W/m

2

Indoor

generated heat

(occupants, lighting

equipment) 35.9%

56.4 W/m

2

157.0 W/m

2

U-12

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)

= 157.0 W/m

2

– 53.0 W/m2= 104.0 W/m

2

●

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 occupant in the office:

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

The heat generated per 1 m

2

of floor space:

Heat generated from occupants = 132.0 W·occupant × 0.2 occupant/m

2

= 26.4 W/m

2

(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 20 - 30 W/m

2

.

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

2

● 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)

= 104.0 – (26.4 + 30.0) = 47.6 W/m

2

U-13

CHAPTER 1 ● Ventilation for Healthy Living

5.3 Ventilation Load During Heating

●

Classification of Heating Load

Class Heat Load

Heat escaping from walls (q

WS)

(a)

Indoor heat

Heat escaping from glass (q

GS)

loss

Heat loss from conduction and convection (q

GS)

Accumulated heat load in walls (q

SS)

(b)

Ventilation

Sensible heat (q

FS)

load

Latent heat (q

FL)

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

●

Heating Load Per Unit Area

When the ventilation air volume per occupant is 25 m3/h, and the number of occupants per 1 m2is 0.2, the heating load
will be approximately 133.7 W/m

2

.

●

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 = 133.7 W/m

2

– 56.0 W/m2= 77.7 W/m

2

●

Ventilation Load

Standard design air conditions in Tokyo

Type of Load Load

Ventilation Air Load

56.0 W/m

2

Internal Heat 77.7 W/m

2

Total 133.7 W/m

2

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

When the load per 1 m2of 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/m

3

× 0.2 occupants/m2× 25 m3/h·occupant × 33.5 kJ/kg = 201.0 kJ/h·m2(56 W/m2)

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

Ventilation

air load 41.9%

56.0 W/m

2

Indoor heat
loss 58.1%

77.7 W/m

2

133.7 W/m

2

Dry Bulb Temp.

Relative Humidity

Wet Bulb Temp. Enthalpy Enthalpy Difference

Heating

Outdoor Air 0 °C 50% –3 °C 5.0 kJ/kg

33.5 kJ/kg

Indoor Air 20 °C 50% 13.7 °C 38.5 kJ/kg

CHAPTER 2

Lossnay Construction and Technology

U-16

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

SA (Supply air diffuser)

Supply fan

RA (Return air)

Exhaust side filter

Lossnay Core

Intake side filter

OA (Outdoor air)

Exhaust fan

EA (Exhaust air)

Note: The dust inlet and outlet are linear in the

actual product.

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.

2. Lossnay Core Construction and Technology

● Simple Construction

The Lossnay core is a cross-air passage total energy recovery unit
constructed from specially treated paper 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 paper. 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 Paper

The paper 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 CO2 from entering the conditioned space.

SA
Supply Air
(Fresh heating/cooling air)

Partition
plate
(Treated
paper)

Spacer plate
(Treated paper)

RA
Return Air
(Dirty heating/cooling air)

Indoors Outdoors

EA
Exhaust Air
(Stale air)

OA
Outdoor air
(Fresh air)

U-17

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 heat that enters
and leaves due to the changes in a 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.

Heat Resistance Coefficients

t1

t2

Ra1

Ra2

Rp

Partition plate
Ra1+Ra2

»Rp

Treated Paper Cu Al

Ra

1

10 10 10

Rp 1 0.00036 0.0006

Ra

2 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

Low humidity side

Partition plate

U-18

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.

SA
Fresh air exhaust
(Fresh heating/cooling air)

RA
Stale air induction
(Dirty heating/cooling air)

Indoors Outdoors

EA
Exhaust air
(Stale air)

OA
Fresh air
induction
(Fresh air)

Item Formula

Temperature recovery
efficiency (%)

ηt =

t

OA - tSA

× 100

t

OA

- tRA

Enthalpy recovery
efficiency (%)

ηi =

i

OA - iSA

× 100

i

OA - iRA

η: Efficiency (%)

t: Dry bulb temperature (°C)

i: Enthalpy (kJ/kg)

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 t

SA = tOA - (tOA - tRA) × ηttEA = tRA + (tOA - tRA) × ηt

Enthalpy i

SA = iOA - (iOA - iRA) × ηiiEA = iRA + (iOA - iRA) × ηi

U-19

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 (°C)

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

(2) Wet Bulb Temperature t’ (°C)

When a dry bulb thermometer is wrapped in a piece of wet
gauze and an ample air flow (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.

(3) Absolute Humidity x (kg/kg’)

Weight (kg) of the water vapor that corresponds to the weight
(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 = P

W

/PWS

× 100

(5) Dew Point t” (°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 (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 0 °C being set at 0.

Temperature (°C)

Absolute humidity x (kg/kg’)

Wet bulb temperature

(dew point) t’ (°C)

Relative humidity ϕ (%)

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

t” °C dew point

Enthalpy i (kJ/kg)

A

t”

Parallel to absolute
temperature scale line

U-20

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.

iSA

iOA

tOA tSA

A

S

O

R

i

RA

iSA

iOA

tRA tRA

S

R

AO

t

SA tOA

XOA

XSA

XRA

XRA

XSA

XOA

iRA

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 × (i

OA - iRA) × ηi

Where γ = Specific weight of the air under standard conditions 1.2 (kg/m

3

)

Q= Treated air volume (m

3

/h)
t= Temperature (°C)
x= Absolute humidity (kg/kg’)
i= Enthalpy (kJ/kg)
η = Energy recovery efficiency (%)

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

Enthalpy (kJ/kg)

Ventilation load

Lossnay Core energy recovery

Enthalpy (kJ/kg)

Ventilation load

Lossnay Core energy recovery

Outdoor air

condition in

winter

Supply air condition of

the Lossnay

Supply air condition of

the Lossnay

Room air

condition

in summer

Outdoor air condition

in summer

Absolute

humidity (kg/kg’)

Room air condition in winter

Dry bulb temperature (°C)

CHAPTER 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-100RX5-E

●

Energy recovery efficiency table (%)

(at 50Hz, high speed) (For summer)

●

Ventilation rate: 1,000 m3/h
(specific gravity of air

ρ

= 1.2 kg/m3)

U-22

CHAPTER 3 ● General Technical Considerations

Lossnay Sensible HRV Conventional

Unit Unit Ventilator Unit

Temperature

76 76 –

(Sensible Heat)

Enthalpy

71 17* –

(Total Heat)

hOA

hSA

hRA

84.6

62.1

52.9

tOA

33

tSA

27.7

tRA

26

R

S

AO

X

OA

0.0201

XSA

0.0134

XRA

0.0105

●

Lossnay Unit
(Supply air diffuser temperature)

= 33°C – (33°C – 26°C) × 0.76 = 27.7°C

(Supply air diffuser enthalpy)

= 84.6 – (84.6 – 52.9) × 0.71 = 62.1 kJ/kg

Heat recovered

(84.6 – 62.1) × 1.2 × 1,000 = 27,000

kJ/kg

= 7.5 kW

Ventilation load

(62.1 – 52.9) × 1.2 × 1,000 = 11,040

kJ/kg

= 3.1 kW

●

Sensible HRV Unit
(Supply air diffuser temperature)

= 33°C – (33°C – 26°C) × 0.76 = 27.7°C

(Supply air diffuser enthalpy)

hSA = 79.2 kJ/kg (from psychrometric chart)

Heat recovered

(84.6 – 79.2) × 1.2 × 1,000 = 6,480

kJ/kg

= 1.8 kW

Ventilation load

(79.2 – 52.9) × 1.2 × 1,000 = 31,560

kJ/kg

= 8.8 kW

[Calculated enthalpy recovery efficiency 1.8 ÷ (1.8 + 8.8) × 100 = 17.0%]

●

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:
(84.6 – 52.9)

×

1.2 ×1,000 = 38,040 kj/h = 10.6 kW

Calculation Example Summer Conditions

Absolute humidity (kg/kg’)

Room air condition in summer

Outdoor air condition

in summer

Supply air condition

of the Lossnay

Dry bulb temperature (°C)

Lossnay energy recovery

Ventilation load

Enthalpy

(kJ/kg)

Supply air

Room air

Indoor Unit

of

Air Conditioner

Lossnay

Unit

Sensible HRV

Unit

Conventional

Ventilator Unit

Dry bulb
temperature

Absolute
humidity

Relative
humidity

Enthalpy

26°C

27.7 27.7 33

13.4 20.1 20.1

58 86 63

62.1 79.2 84.6

7.5 8.8 0

3.1 1.8 10.6

71 17 100

10.5 g/kg’

50%

52.9 kj/kg

Outdoor air

Exhaust air

Dry bulb
temperature
Absolute
humidity
Relative
humidity

Enthalpy

33°C

20.1 g/kg’

63%

84.6 kj/kg

Dry bulb temperature (°C)

Absolute humidity (g/kg’)

Relative humidity (%)

Enthalpy (kJ/kg)

Ventilation load (kW)

Ventilation load ratio (%)

Total energy recovered (kW)

* Calculated volume under conditions below.

(2) Heating During Winter

Conditions:

●

Model LGH-100RX5-E

●

Energy recovery efficiency table (%)

(at 50Hz, high speed) (For winter)

●

Ventilation rate: 1,000 m3/h
(Specific gravity of air

ρ

= 1.2 kg/m3)

U-23

CHAPTER 3 ● General Technical Considerations

Lossnay Sensible HRV Conventional

Unit Unit Unit

Temperature

80 80 –

(Sensible Heat)

Enthalpy

72.5 49* –

(Total Heat)

Supply air

Room air

Indoor Unit

of

Air Conditioner

Lossnay

Unit

Sensible HRV

Unit

Conventional

Ventilator Unit

Dry bulb
temperature

Absolute
humidity

Relative
humidity

Enthalpy

20°C

16 16 0

5.2 1.9 1.9

46 17 50

29.2 21 4.7

8.2 5.5 0

3.1 5.8 11.3

72.5 49 100

7.3 g/kg’

50%

38.5 kj/kg

Outdoor air

Exhaust air

Dry bulb
temperature
Absolute
humidity
Relative
humidity

Enthalpy

0°C

1.9 g/kg’

50%

4.7 kj/kg

Dry bulb temperature (°C)

Absolute humidity (g/kg’)

Relative humidity (%)

Enthalpy (kJ/kg)

Ventilation load (kW)

Ventilation load ratio (%)

Total energy recovered (kW)

●

Lossnay Unit
(Supply air diffuser temperature) tSA=

(20°C – 0°C) × 0.8 + 0°C = 16°C

(Supply air diffuser enthalpy) hSA= (38.5 – 4.7) × 0.725 + 4.7

= 29.2 kj/kg

Heat recovered (29.2 – 4.7) × 1.2 × 1,000

= 29,400 kj/h = 8.2 kW

Ventilation load (38.5 – 29.2) × 1.2 × 1,000

= 11,160 kj/h = 3.1 kW

●

Sensible HRV Unit
(Supply air diffuser temperature) tSA=

(20°C – 0°C) × 0.8 + 0°C = 16°C

(Supply air diffuser enthalpy) hSA= 21 kj/kg

(from psychrometric chart)

Heat recovered (21 – 4.7) × 1.2 × 1,000

= 19,560 kj/h = 5.5 kW

Ventilation load (38.5 – 21) × 1.2 × 1,000

= 21,000 kj/h = 5.8 kW

[Calculated enthalpy recovery efficiency 5.4 ÷ (5.4 + 5.8) × 100 = 48%]

●

Conventional Ventilator Unit
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
(38.5 – 4.7) × 1.2 × 1,000 = 40,560 kj/h = 11.3 kW

Calculation Example Winter Conditions

hRA

iOA

tOA

0

tSA16tRA

20

R

S

O

A

X

RA 0.0073

XSA 0.0052

XOA 0.0019

hSA

38.5

4.7

29.2

Absolute humidity (kg/kg’)

Outdoor air

condition in

winter

Room air condition

in winter

Supply air condition

of the Lossnay

Dry bulb temperature (°C)

Lossnay

energy recovery

Ventilation load

Enthalpy

(kJ/kg)

* Calculated volume under conditions below .

U-24

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) = m3/Hr

●

Outdoor air volume (OA) = m3/Hr

●

Air volume ratio (RA/OA) =

●

Air conditions

●

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: yen/kWh

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

(2) Lossnay Model

●

Model name:

●

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

●

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 filters)

●

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

(3) Indoor Blow Air Conditions

Season Winter Heating Summer Cooling

Dry bulb Wet bulb Relative Absolute Enthalpy Dry bulb Wet bulb Relative Absolute Enthalpy

Item temp. temp. humidity humidity i kJ/kg temp. temp. humidity humidity i kJ/kg

DB [°C] WB [°C] RH [%]×[kg/kg’] (kcal/kg’) DB [°C] WB [°C] RH [%]×[kg/kg’] (kcal/kg’)

Outdoors

Indoors

Heating Cooling

= (Indoor temperature – outdoor air temperature) × = Outdoor air temperature – (outdoor air

Temperature [°C]

energy recovery efficiency + outdoor air temperature – indoor temperature) ×
temperature energy recovery efficiency

==

= (Indoor enthalpy – outdoor air enthalpy) × = Outdoor air enthalpy – (outdoor air

Enthalpy [kJ/kg]

enthalpy recovery efficiency + outdoor air enthalpy – indoor enthalpy) ×
enthalpy enthalpy recovery efficiency

==

Data obtained from

●

Dry-bulb temperature = °C

●

Dry-bulb temperature = °C

above equation

●

Wet-bulb temperature = °C

●

Wet-bulb temperature = °C

and

●

Relative humidity = %

●

Relative humidity = %

psychometric chart

●

Absolute humidity = kg/kg’●Absolute humidity = kg/kg’

●

Enthalpy = kg/kg●Enthalpy = kg/kg

U-25

CHAPTER 3 ● General Technical Considerations

(4) Ventilation Load and Energy Recovery

Heating Cooling

Ventilation load without

= Air specific gravity × ventilation volume = Air specific gravity × ventilation volume

Lossnay (q

1)

× (indoor enthalpy

–

outdoor air enthalpy) × (outdoor air enthalpy – indoor enthalpy)

==

=Ventilation load (q

1) = Ventilation load (q1)

× ( 1 – enthalpy recovery efficiency) × ( 1 – enthalpy recovery efficiency)
Ventilation load with = =
Lossnay (q

2)or or

= Air specific gravity × ventilation volume = Air specific gravity × ventilation volume

× (indoor enthalpy

–

indoor blow enthalpy) × (indoor blow enthalpy – indoor enthalpy)

=q

1

–

q

2 =q1

–

q2

=

–

=

–

Energy recovery (q3)

==

or or

=Ventilation load (q

1)=Ventilation load (q1)

× enthalpy recovery efficiency × enthalpy recovery efficiency

● Ventilation load = W = % ● Ventilation load = W = %

Ventilation load (%)

● Ventilation load with Lossnay ● ventilation load with Lossnay

= W = % = W = %

● Energy recovered = W = % ● Energy recovered = W = %

(5) Recovered Money (Power Rates)

Heating Cooling

=

Energy recovered: kW × Unit price ¥/kWh ×

=

Energy recovered: kW × Unit price ¥/kWh ×

Cost savings

operation

time Hr/year = kW ×

¥

/

kWh

×

operation

time Hr/year = kW ×¥/

kWh

×

(

yen)

= Hr/year = Hr/year
==

U-26

CHAPTER 3 ● General Technical Considerations

3. Psychrometric Chart

0.00.000

0.001

0.002

0.003

0.004

0.005

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

0.033

0.034

0.035

0.036

0.037

0.1

0.5

1.0

1.5

2.0

2.5

3.0

3.5

4.0

4.5

5.0

5.5

Vapor pressure Pw [kPa]

Absolute humidity x [kg/kg(DA)]

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

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

—7—8 —5—6 1

18

19

20

55

60

65

70

22

21

23

24

25

75

80

26

27

85

90

28

29

95

100

105

110

31

115

120

33

32

34

35

125

30

50

45

40

35

11

10

9

8

7

6

4

5

3

2

1

0

—1

—2

—4

—5

—5

0

5

10

90

80

70

60

50

40

30

25

60

55

65

70

75

80

85

95

90

85

80

75

70

65

60

55

50

50

45

40

40

45

35

30

25

20

15

10

5

35

30

25

20

15

20

10

5

15

15

25

30

20

—8

10

5

0

15

20

25

30

12

13

14

15

16

17

—40000

40000

20000

15000

10000

7000

6000

5000

4500

4200

4000

3800

—20000

—10000

—5000

—2000

—1000

—500

0

500

1000

1200

1400

1600

1800

2000

2200

2400

2600

2800

3000

3200

3400

3600

3800

1.0

0.9

0.8

0.7

0.6

0.5

0.4

0.3

Comparative enthalpy h [kJ/kg(DA)]

Humid air psychrometric chart

(-10 to +50¡C, atmospheric pressure 101.325 kPa)

Heat water ratio u = –– [kJ/kga]

dh

dx

Sensible heat ratio SHF

Saturation [%]

0.94

0.92

0.93

0.96

0.95

Wet bulb temperature t' [¡C]

Relative humidity [%]

Specific capacity v [m

3

/kg(DA)]

Dry bulb temperature t [¡C]

Water

Chilled

U-27

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/cm2with 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 flow, and
then connected to the impingers outside the ducts. The impingers are filled with 100 mL physiological salt
solution. The airborne bacteria in the duct air are sampled at the rate of 10L air/minute for three minutes.

(5) Test Bacteria

The bacteria used in this test are as followed;

Bacillus subtilis: IFO 3134
Pseudomonas diminuta: IFO 14213 (JIS K 3835: Method of testing bacteria trapping capability of precision
filtration film elements and modules; applicable to precision filtration film, etc. applied to air or liquid.)

(6) Test Result

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

Sprayer

Impinger

Impinger

Impinger

Fan

Fan

Safety cabinet

Impinger

LOSSNAY Core

HEPA Filter

U-28

CHAPTER 3 ● General Technical Considerations

Table 1 Test Results with Bacillus Subtilis (CFU/30L air)

No. A B C D

1 5.4 × 10

4

5.6 × 10

4

< 10

3

< 10

3

2 8.5 × 10

3

7.5 × 10

3

< 10

3

< 10

3

3 7.5 × 10

3

< 10

3

< 10

3

< 10

3

4 1.2 × 10

4

1.2 × 10

4

< 10

3

< 10

3

5 1.8 × 10

4

1.5 × 10

3

< 10

3

< 10

3

Average 2.0 × 10

4

1.5 × 10

4

< 10

3

< 10

3

Table 2 Test Results with Pseudomonas Diminuta (CFU/30L air)

No. A B C D

1 3.6 × 10

5

2.9 × 10

5

< 10

3

< 10

3

2 2.5 × 10

5

1.2 × 10

5

< 10

3

< 10

3

3 2.4 × 10

5

7.2 × 10

5

< 10

3

< 10

3

4 3.4 × 10

5

8.4 × 10

5

< 10

3

< 10

3

5 1.7 × 10

5

3.8 × 10

5

< 10

3

< 10

3

Average 2.7 × 10

5

4.7 × 10

5

< 10

3

< 10

3

(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 filter
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 filtered by the HEPA filter) 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

CHAPTER 3 ● General Technical Considerations

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.

5. Lossnay Core Fire : retardant property

U-30

CHAPTER 3 ● General Technical Considerations

6. Lossnay Core Sound Reducing Properties Test

Because the Lossnay Core is made of paper 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.

Test number

Sound Reducing Effect Test Results

Standard

Test Method

Client

Name

Address

Trade name

Main composition

Manufacture date

Size (unit : mm)

Note

Date of test
Sound transmitting size
Air temperature, Relative humidity

May 18, 2001
φ254 mm ✕ 2

22.0°C, 62%RH (Receiving room)

100
125
160
200
250
315
400
500
630

800
1000
1250
1600
2000
2500
3150
4000
5000

83.3

83.8

85.5

86.0

86.1

85.0

86.2

84.4

84.7

85.5

87.0

89.2

89.3

90.7

92.8

83.4

95.0

95.0

59.3

62.8

61.0

58.7

58.3

57.0

54.3

49.4

50.7

48.7

47.7

47.7

47.4

47.0

48.2

48.2

48.8

47.6

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

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

10

6

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

11

6
10
13
13
12
16
19
17
20
22
24
23
25
25
25
25
26

Center

frequency

(Hz)

Equivalent

absorption

area in receiving

room A (m2)

Sound

transmission

loss

TL (dB)

Test

laboratory

Revised sound
transmission

loss

TLc (dB)

Average sound pressure level (dB)

Level

difference D

Receiving

room Lr

Source

room Ls

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.)

Test SpecimenTest Results

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
building elements".

Notes:

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

2. Test specimen area (Sound transmitting area) is:
S = 0.10134m2 (φ254mm ✕ 2) for calculating (revised) sound transmission

loss.

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

- 4000Hz)....18.4dB

Iwao Kurahashi (Head)
Takao Waki (Section chief)
Mitsuo Morimoto (Section chief)

Joint adapter in the sound receiving room side
(Portion A in ANNEXED DRAWING No.1) had
been filled with oil clay and then covered with
onefold aluminum tape, sound insulation sheet
and glass wool around duct successively.

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

Responsible parties

Sound source side

Sound source sideSound receiving side

(Reverberation room No. 2)

178.5m

3

(Reverberation room No. 3)

180.0m

3

Volume

Test specimen

Test
specimen

SP.

Sound receiving side

Section

300

5560

Air layer (t50)

Chain block (2t)

Neoprene rubber

Test specimen

Filled with sand

F. L.

Filled inside with sand
Mortared both sides (15mm)

Cavity concrete block (t190)

300

Amplifier2 ch selector

MIC.

EqualizerReal time analyzer

Noise generator

Fig. 1 Testing setup (Unit : mm)

Computer system

Printer

Air-to-Air Energy

Recovery Ventilator

LGH-100RX

3-E

Level difference between
the source room and the
receiving room

Revised sound
transmission loss

Sound transmission loss

70

60

50

40

30

20

10

0

125 250 500 1000 2000 4000

Center frequency (Hz)

Sound transmission loss (dB)

U-31

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 floors

(3) Total Floor Space : 38,893 m

2

(4) Reference Floor Space : 1,388 m

2

7.2 Specifications of Installed Ventilation Equipment

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

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

: 340 kT, heating 1,630 kW

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

”
LS-200 × 18 units installed in penthouse.
Outdoor air treatment volume: 46,231 CMH,
Exhaust air treatment volume: 54,335 CMH.

+

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

AC

AC

AC

4080

4300

10040

2000

3200

700

1300 1300

Lossnay

Lossnay

Lossnay

Lossnay

SA

EA

O A

RA

Lossnay Duct System Diagram Diagram of Lossnay Penthouse Installation

Unit (mm)

Exhaust air

OA side bypass damper

Lossnay

RA fan

(for

exhaust)

Outdoor
air

OA fan

(for intake)

RA side

bypass damper

U-32

CHAPTER 3 ● General Technical Considerations

7.3 Lossnay Operation

(1) Unit Operation Began : September 1972

Daily Operation Began : 7:00

Average daily operation: 11 hours

Daily Operation Stops : 18:00

(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 500 m

3

/hr, and the measurement point was

±200 m

3

/hr of that value.

300

0

10

20

60

30

70

80

90

500 700

Changes Detected in the Lossnay Core

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 150 to 160 Pa at 500 m

3

/hr, which was a 10 Pa increase. The exchange efficiencies had

decreased slightly to above 500 m

3

/hr, however, this is considered to be insignificant 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.

}

Data from delivery (1974)
Data from 1983

Treated air volume (m3/h)

Energy recovery
efficiency

Enthalpy recovery
efficiency during heating

Static pressure loss

Static pressure loss (mmH2O) Recovery efficiencies (%)

U-33

CHAPTER 3 ● General Technical Considerations

8. Comparing Energy Recovery Techniques

Basic Methods of Total Energy Exchangers

Country of

Type Method Air flow

development

Static Conductive Cross-flow Japan

Energy recovery (Mitsubishi Lossnay) transmission type
principle

Rotary type Heat accumulation/ Counterflow 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, drive motor
and housing.
A large quantity of moisture absorbent material (lithium chloride,
etc.) is applied onto the rotor, and humidity is transferred.
The rotor rotates eight times a minute by the drive motor.

●

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 airflow. Because one of the plates
is slightly shifted, part of the ventilation air always flows into the
exhaust air passage to prevent the exhaust air and ventilation air
from mixing. (A balanced pressure difference is required.)

A

Vs

B

Vr

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

Approx. ø1.5mm

Purge sector

Exhaust

Fresh air

Drive motor

Power supply
AC 200 V 50/60 Hz

Rotor

Bearing

Supply air Fresh air

Return air Exhaust

Drive motor

Room side

Purge sector

Fresh air

Return air

Rotor rotation direction

U-34

CHAPTER 3 ● General Technical Considerations

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

Specification

Construction/
Principle

Moving Parts

Material Quality

Prefilter

Element Clogging

Air Leakage
Gas Transmission
Rate

Bacteria
Transmission Rate

Operation During
Off Seasons

Maintenance

Life

Model is
Available

Standard Treatment
Air Volume

Enthalpy Recovery
Efficiency

Pressure Loss

Installation Space
(W × D × H) (mm)

Static-type

Conductive transmission-type: cross-flow
Static-type transmission total energy recovery unit
with orthogonally layered honeycomb-shaped
treated paper 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

Treated paper

Required (periodic cleaning required)

● 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 : 28%,

hydrogen sulfide : approx. 6.7%)

● 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.)

o

Available from small to large. Example

o

Characteristic design of small LU-1605
and medium models are possible.
Large models are easy to
match to a machine room layout

.

40 to 25,000 m

3

/h 8,000 m3/h

Temperature: 77%
Enthalpy
Heating: 71%
Cooling: 66%

170 Pa

Effective for small to medium capacity

600 × 2100 × 2540

(Layout depends on combination chosen.)

Rotary-type

Heat accumulation/humidity accumulation­type: counterflow
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 airflows into a honeycomb passage.

× Supply air and exhaust airflows go into the same air

passage because of the rotary-type construction.

× Rotor driven with belt by gear motor

Rotor core (8 rpm)

Treated paper, aluminum plates, etc.

Required (periodic cleaning required)

×

Occurs (Dust is smeared into element air passage filter.)
(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%,

hydrogen sulfide : approx. 3.2-4%)

× 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)
(In theory, operation is possible by stopping the rotation,
but the core will over-absorb, and cause damage.)

Core

cleaning: Once every one to two years
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 Example

× Small models are difficult to EV-1500

design because of the rotor
magnitude.

o

100 to 63,000 m3/h 8,000 m3/h

74%

180 Pa

Large capacity models are 320 × 1700 × 1700
effective

Measure of useability

●

: Higho: Average×: Poor

CHAPTER 4

Characteristics

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

Increases

(such as a spiral)

U-36

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

Estimated static pressure loss curve
obtained from 1 and 2

3

Air volume

Static

pressure

4 Intersection with air volume static

pressure characteristic curve

5 Air volume at application point

2 Total static

pressure loss

6 Static pressure loss at

application point

1 Required air

volume

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 65 Pa is applied

to Point A, and the air volume is 500 m

3

/h. The duct resistivity
curve shows how the static pressure is applied when a duct is
connected to the Lossnay. Thus, the L = 9.97 m duct resistivity
curve in the diagram shows how the static pressure is applied
when a 10 m duct is connected. Intersecting Point A on the
Lossnay Q-H curve is the operation point.

Duct Resistivity Curve

The duct resistivity curve shows how much static pressure a duct will apply on the Lossnay.

In general, the relation between the duct and static pressure is as follows:

500m3/h

65 Pa

L =

10m

A

20 m

15 m

10 m

5 m

Q-H curve

Static pressure

Duct resistivity curve

Air volume

Air volume

Static pressure

(Duct length)

Example

How to read Table 3

Convert a rectangular pipe (in this case, a square pipe:
520 mm each side, for example) to a round pipe in
diameter, using this table.
The maximum value for the short side of rectangular pipe
is 17 in the table, therefore divide 520 by 100 and it
results in 5.2. The round pipe diameter 5.6 is shown by
the cross-point of two lines: long side of rectangular pipe

5.2 and short side of rectangular pipe 5.2. Finally, multiply

5.6 by 100 and find that the rectangular (square) pipe is
equal to the ø 560 mm round pipe.

1

1234567891011121314151617

2

3

4

5

6

7

8

9

10

11

12

13

14

15

16

17

18

19

20

21

21

20

19

18

17

16

15

14

13

12

11

10

9

8

7

6

22

23

24

25

5

5・6

4

3

2

1

Long side of

rectangular pipe

Round pipe diameter

Round pipe diameter having equal hydraulic radius

Short side of
rectangular pipe

5.2

5.2

U-37

CHAPTER 4 ● Characteristics

Reference

Pressure loss caused by velocity (Pa)

=

r

× V

2

=

1.2
× (velocity)

2

22

r:Air weight 1.2 kg/m

3

v:Velocity (m/s)

2.2 Calculating of Duct Pressure Loss

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

{

(2) Obtaining the Duct Resistivity

Table 4. Round Duct Friction Loss

(steel plate duct, inner roughness ε = 0.18 mm)

(1)

Calculating a Rectangular Pipe

Table 3. Conversion Table from

Rectangular Pipe to Round Pipe

100

200

400

600

800

1,000

2,000

4,000

6,000

8,000

10,000

20,000

40,000

60,000

80,000

100,000

200,000

400,000

600,000

800,000

1,000,000

0.1 0.2 0.4 0.6 0.8 1.0 2.0 4.0 6.0 8.0 10 20 30 40 50 60 80 100

0.1 0.2 0.4 0.6 0.8 1.0 2.0 4.0 6.0 8.0 10 20 30 40 50 60 80 100

V=50m/s

40

V=50

30

25

20

15

10

9

8

7

6

5

4

3

2.0

3

5

0

d=500cm

d

=

1

0

0

c

m

d=400cm

3

0

0

2

5

0

2

0

0

1

8

0

1

6

0

1

4

0

1

2

0

9

0

8

0

7

0

6

0

5

0

4

5

4

0

3

5

3

0

2

5

20

1

8

1

6

1

4

1

2

1

0

9

8

7

6

5

200

100

40

30

25

20

15

10

9

8

7

6

5

0

4

0

3

0

2

0

1

0

How to read Table 4

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

(Outline of Table 4)

Air volume (m

3

/h)

Friction loss (Pa/m)

Friction loss

180

160

140

120

100

80

60

40

20

24 6 81012 14 16 18

560mm

Air volume: 7000 m

3

/h

Duct diameter

Average

velocity

8 m/s

Resistance

1.17Pa/m

Outdoor air pressure (Pa)

Velocity (m/s)

U-38

CHAPTER 4 ● Characteristics

Data obtained from Table 4 must then be corrected for duct type at various velocities using Table 5 below.

Ta ble 5. Friction Coefficient Compensation Table

An alternative, more detailed method for determining the pressure loss in duct work uses the following formula:

Inside Surface of Duct Example

Average Velocity (m/sec.)

5101520

Very Rough Concrete Finish 1.7 1.8 1.85 1.9

Rough Mortar Finish 1.3 1.35 1.35 1.37

Very Smooth Drawn Steel Pipe, Vinyl Pipe 0.92 0.85 0.82 0.8

Round pipe section pressure loss

∆p = λ

·· ·

v

2

(Pa)

∆p = C

··

v

2

(Pa)

= 0.6 C ·v

2

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

: Duct length (m)

ρ

: Air weight (1.2 kg/m2)

v:Wind velocity (m/s)

R

d

ρ

2

ρ

2

R

Duct

No.

Area

Outline Diagram

Conditions

C

Value

R/D = 0.5 0.73 43D

90° =

0.75

0.38 23D

1 Smooth = 1.0 0.26 15D

Elbow = 1.5 0.17 10D

= 2.0 0.15 9D

W/D R/D

0.5 1.30 79D

0.5

0.75 0.47 29D

Rectangular 1.0 0.28 17D

2 Radius 1.5 0.18 11D

Elbow 0.5 0.95 57D

1-3

0.75 0.33 20D

1.0 0.20 12D

1.5 0.13 8D

R/D

0.5 0.70 42D

Rectangular 1

0.75 0.16 10D

Vaned

1.0 0.13 8D

3

Radius

1.5 0.12 7D

Elbow

0.5 0.45 27D

2

0.75 0.12 7D

1.0 0.10 6D

1.5 0.15 9D

90°

4 Miter 0.87 53D

Elbow

Rectangular

5 Square 1.25 76D

Elbow

Rectangular

6

Vaned

0.35 21D

Square
Elbow

Rectangular

7

Vaned
Square
Junction

Same loss as circular duct.

Rectangular

Velocity is based on inlet.

8

Vaned
Radius
Junction

45°

9 Smooth

Elbow

a = 5° 0.17 10D

10° 0.28 17D
20° 0.45 27D

10 Expansion 30° 0.59 36D

40° 0.73 43D
Loss is for
hV

1 - hV2

a = 30° 0.02 1D

45° 0.04 2D

11 Contraction 60° 0.07 4D

Loss is for
V

2

Duct

No.

Area

Outline Diagram

Conditions

C

Value

12 Transformer 0.15 9D

Short

13

Entrance

0.50 30D

Short

14

Exit

1.0 60D

Bell-shaped

15

Entrance

0.03 2D

Bell-shaped

16

Exit

1.0 60D

Re-entering

17

inlet

0.85 51D

V

1

/V2 = 0 2.8 170D

0.25 2.4 140D

Sharp edge,

0.50 1.9 110D

18

round orifice

0.75 1.5 90D
1 1.0 60D

Loss is for
V

2

20° 0.02

Pipe inlet

40° 0.03

19

(with

β 60° 0.05

circular

90° 0.11

hood)

120° 0.20

20° 0.03

Pipe inlet

40° 0.08

20

(with

β 50° 0.12

rectangular

90° 0.19

hood)

120° 0.27

V

1/V2 = 0 0.5 30D

0.25 0.45 27D

Short

0.50 0.32 19D

21

contraction

0.75 0.18 11D

Loss is for
V

2

V

1/V2 = 0 1.0 60D

0.20 0.64 39D

Short

0.40 0.36 22D

22

expansion

0.60 0.16 9D

0.80 0.04 2D
Loss is for
V

1

Suction
inlet

0.2 35

23 (punched

0.4 7.6

narrow

0.6 3.0

plate)

0.8 1.2

U-39

CHAPTER 4 ● Characteristics

(3) How to Calculate Curved Sections in Ductwork

Table 6. Pressure Losses in Each Duct Area

Length of

Equivalent

Round

Pipe

No. of
vanes

With or without
vanes,
rectangular or
round

1/2 times value
for similar 90°

Length of

Equivalent

Round

Pipe

Free are ratio

14° or less

D

High notch air volume

U-40

CHAPTER 4 ● Characteristics

3. How to Obtain Efficiency from Characteristic Curves

How to Read Characteristic Curve

●

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

90

0.5 0.6 0.7

50 60 70 80 90 100

0.8 0.9 1.0 1.1 1.4

1.2 1.3

80

70

60

50

40

Efficiencyobtainedfromsupplysideairvolume(%)

Energyrecovery

efficiency

(%)

Airvolumeratio=

Exhaustairvolume
Supplyairvolume

Correctedenergyrecoveryefficiency(%)

Recovery
efficiency

Static pressure
outside unit

Temperature

recovery efficiency

Enthalpy recovery efficiency

(heating)

Enthalpy recovery efficiency

(cooling)

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

Pipe length

1

2

3

Recovery efficiency

Low notch air volume

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

Static pressure outside unit

Efficiency obtained
with air volume on
supply side from
characteristic curve

Air volume ratio =

Exhaust air volume

Supply air volume

Supply side efficiency

after correction

5

4

Energy Recovery Efficiency Correction Curve

U-41

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.

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*2and 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.

Sound level (dB)

Frequency (Hz)

Minimum audible valve

120 dB

100

–200

–20

–2

–0.2

–0.02

–0.002

–0.0002

80

60

40

20

4.2

Response (dB)

Frequency (Hz)

Characteristic A

Characteristic C

Flat characteristic

Sound

pressure

(Pa)

Sound

strength

(W / cm2)

ISO Audio Perception Curve

U-42

CHAPTER 4 ● Characteristics

Room Application

dB

NC Value Room Application

dB

NC Value

Broadcasting studio 25 15 - 20 Cinema 40 30

Music hall 30 20 Hospital 35 30

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

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 specific 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

●

Tolerable Sound Levels and NC Values According to Room Application

Frequency band (Hz)

Level (dB)

Frequency (Hz)

SPL (dB)

Min. audible limit

U-43

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

Normal
machine
factory

(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 Train 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

people

30 Peaceful In broadcasting studio

20 Very quiet Sound of leaves

brushing against

10 each other

0

Source: “Heibon Sha, Industrial Encyclopedia”

Computer
room

Typing
room

Many
occupants

Few
occupants

Subway

Overhead
train

Passenger
car

Business
and
industrial
district

Suburb

Quiet
night

Factory

Tr ansportation facilities

Conversation

Residential area

Office

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.

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

PWL : Sound source power level (dB)

SPLo : Measured sound pressure in anechoic

chamber (dB)

ro : Distance from the unit to measuring point (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 finished ceiling. is the echo sound of .

3) Position of Sound Source and Sound Value

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

(i) (ii)

SPL :

Sound pressure level at reception point [dB]

PWL : Power level of sound source [dB]

Q:Directivity factor (Refer to Fig. 3)

r:Distance from sound source [m]
R:Room constant [R = αS/(1 – α)]
α :Average sound absorption ratio in room

(Normally, 0.1 to 0.2)

S:Total surface area in room [m

2

]

U-44

CHAPTER 4 ● Characteristics

Position of Sound Source

Center of room

Center of ceiling

Edge

Corner

a

b

c

d

Q

1

2

4

8

Fig. 1.

Fig. 2.

Fig. 3.

(Position of Sound Source and Directivity Factor Q)

3

1

Q

4πr

2

4
R

{}

Unit

ro

Supply air diffuser
(return grille)

Supply air diffuser
(return grille)

c

b

a

d

Unit

U-45

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

SPL1/10

+ 10

SPL2/10

)

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

(III)

●

The average sound absorption rate in the room and the
ceiling transmission loss differ according to the frequency,
so formula (II) is calculated for each 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).)

(2) Reducing Lossnay Unit Operating Sound

1) When the airflow 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 specifications if

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

(Ex. ø 250 → ø 150, ø 200 → ø 100)

b) Curves in aluminum flexible 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.)

125

250

500

1,000

2,000

4,000

Lauan Plywood
(12mm thick)

23

20

21

23

26

24

—

Fig. 4. Large Unit Installation (Example)

Fig. 5. Countermeasure (Example)

Transmission Loss in Ceiling Material (dB) Example

Average

20

10

11

19

26

34

42

22

12

15

21

28

35

39

Plaster Board
(7mm thick)

Plaster Board
(9mm thick)

Frequency band (Hz)

1

3

a) d)

a) b)

c) b)

U-46

CHAPTER 4 ● Characteristics

2)

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.)

3)

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.

Fig. 6 Sound from Supply Air Diffuser

Fig. 7 Countermeasure (Example)

Fig. 8 Additional Countermeasure (Example)

a) b) c)

a) b)

a) b)

U-47

CHAPTER 4 ● Characteristics

5. NC Curves

10

15

20

25

30

35

40

45

50

55

60

65

70

75

80

85

90

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

Octave band frequency near center (Hz)

Octave band sound pressure level (dB)

NC-70

1.5 m below
Measurement

point

NC-10

NC-20

NC-30

NC-40

NC-50

NC-60

Extra
high
High

Low

Extra
Low

LGH-15RX5-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 : 220 V 50 Hz Power supply : 240 V 50 Hz

LGH-25RX5

-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 : 220 V 50 Hz Power supply : 240 V 50 Hz

LGH-35RX5-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 : 220 V 50 Hz Power supply : 240 V 50 Hz

10

15

20

25

30

35

40

45

50

55

60

65

70

75

80

85

90

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

Octave band frequency near center (Hz)

Octave band sound pressure level (dB)

1.5 m below
Measurement

point

NC-10

NC-20

NC-30

NC-40

NC-50

NC-60

NC-70

Extra
high

Low

Extra
Low

High

10

15

20

25

30

35

40

45

50

55

60

65

70

75

80

85

90

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

Octave band frequency near center (Hz)

Octave band sound pressure level (dB)

1.5 m below
Measurement

point

Extra
high

High

Low

Extra
Low

NC-20

NC-30

NC-40

NC-50

NC-60

NC-10

NC-70

10

15

20

25

30

35

40

45

50

55

60

65

70

75

80

85

90

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

Octave band frequency near center (Hz)

Octave band sound pressure leve l (dB)

1.5 m below
Measurement

point

Extra
high
High

Low

Extra
Low

NC-10

NC-20

NC-30

NC-40

NC-50

NC-60

NC-70

10

15

20

25

30

35

40

45

50

55

60

65

70

75

80

85

90

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

Octave band frequency near center (Hz)

Octave band sound pressure level (dB)

1.5 m below
Measurement

point

Extra
high

High

Low

Extra
Low

NC-10

NC-20

NC-30

NC-40

NC-50

NC-60

NC-70

10

15

20

25

30

35

40

45

50

55

60

65

70

75

80

85

90

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

Octave band frequency near center (Hz)

Octave band sound pressure level (dB)

1.5 m below
Measurement

point

Extra
high
High

Low

Extra
Low

NC-10

NC-20

NC-30

NC-40

NC-50

NC-60

NC-70

U-48

CHAPTER 4 ● Characteristics

10

15

20

25

30

35

40

45

50

55

60

65

70

75

80

85

90

NC-10

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

Octave band frequency near center (Hz)

Octave band sound pressure level (dB)

1.5 m below
Measurement

point

Extra
high

High

Low

Extra
Low

NC-20

NC-30

NC-40

NC-50

NC-60

NC-70

LGH-50RX5-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 : 220 V 50 Hz Power supply : 240 V 50 Hz

LGH-65RX5-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 : 220 V 50 Hz Power supply : 240 V 50 Hz

LGH-80RX5-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 : 220 V 50 Hz Power supply : 240 V 50 Hz

10

15

20

25

30

35

40

45

50

55

60

65

70

75

80

85

90

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

Octave band frequency near center (Hz)

Octave band sound pressure level (dB)

1.5 m below
Measurement

point

Extra
high

High
Low

Extra
Low

NC-10

NC-20

NC-30

NC-40

NC-50

NC-60

NC-70

Extra
high

High

Low

Extra
Low

NC-10

NC-20

NC-30

NC-40

NC-50

NC-60

NC-70

10

15

20

25

30

35

40

45

50

55

60

65

70

75

80

85

90

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

Octave band frequency near center (Hz)

Octave band sound pressure level (dB)

1.5 m below
Measurement

point

Extra
high
High

Low

Extra
Low

10

15

20

25

30

35

40

45

50

55

60

65

70

75

80

85

90

NC-10

NC-20

NC-30

NC-40

NC-50

NC-60

NC-70

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

Octave band frequency near center (Hz)

Octave band sound pressure level (dB)

1.5 m below
Measurement

point

Extra
high

High

Low

Extra
Low

10

15

20

25

30

35

40

45

50

55

60

65

70

75

80

85

90

NC-10

NC-20

NC-30

NC-40

NC-50

NC-60

NC-70

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

Octave band frequency near center (Hz)

Octave band sound pressure level (dB)

1.5 m below
Measurement

point

10

15

20

25

30

35

40

45

50

55

60

65

70

75

80

85

90

NC-10

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

Octave band frequency near center (Hz)

Octave band sound pressure level (dB)

1.5 m below
Measurement

point

Extra
high
High
Low

Extra
Low

NC-20

NC-30

NC-40

NC-50

NC-60

NC-70

U-49

CHAPTER 4 ● Characteristics

10

15

20

25

30

35

40

45

50

55

60

65

70

75

80

85

90

NC-10

NC-20

NC-30

NC-40

NC-50

NC-60

NC-70

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

Octave band frequency near center (Hz)

Octave band sound pressure level (dB)

1.5 m below
Measurement

point

Extra
high
High

Low

Extra
Low

LGH-100RX5-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 : 220 V 50 Hz Power supply : 240 V 50 Hz

LGH-150RX5-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 : 220 V 50 Hz Power supply : 240 V 50 Hz

LGH-200RX5-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 : 220 V 50 Hz Power supply : 240 V 50 Hz

10

15

20

25

30

35

40

45

50

55

60

65

70

75

80

85

90

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

Octave band frequency near center (Hz)

Octave band sound pressure level (dB)

1.5 m below
Measurement

point

NC-10

NC-20

NC-30

NC-40

NC-50

NC-60

NC-70

Extra
high
High

Low

Extra
Low

Extra
high
High
Low

10

15

20

25

30

35

40

45

50

55

60

65

70

75

80

85

90

NC-10

NC-20

NC-30

NC-40

NC-50

NC-60

NC-70

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

Octave band frequency near center (Hz)

Octave band sound pressure level (dB)

1.5 m below
Measurement

point

10

15

20

25

30

35

40

45

50

55

60

65

70

75

80

85

90

NC-10

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

Octave band frequency near center (Hz)

Octave band sound pressure level (dB)

1.5 m below
Measurement

point

Extra
high
High
Low

NC-20

NC-30

NC-40

NC-50

NC-60

NC-70

High

Low

Extra
high

10

15

20

25

30

35

40

45

50

55

60

65

70

75

80

85

90

NC-10

NC-20

NC-30

NC-40

NC-50

NC-60

NC-70

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

Octave band frequency near center (Hz)

Octave band sound pressure leve l (dB)

1.5 m below
Measurement

point

10

15

20

25

30

35

40

45

50

55

60

65

70

75

80

85

90

NC-10

NC-20

NC-30

NC-40

NC-50

NC-60

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

Octave band frequency near center (Hz)

Octave band sound pressure level (dB)

1.5 m below
Measurement

point

Extra
high

High
Low

NC-70

CHAPTER 5

System Design Recommendations

U-52

CHAPTER 5 ● System Design Recommendations

1. Lossnay Operating Environment

Main Unit Installation Conditions Outdoor Air and Exhaust Air Conditions

-10°C to 40°C -15°C to 40°C

Commercial use Lossnay

RH80% or less RH80% or less

1.2 In Cold Climates with Outdoor Temperature of –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’.

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. General-purpose Lossnay units that use
treated paper cannot be installed in those types of environments.

1.4 Other Special Conditions

A

A’

C’

C

B

Saturation curve

Dry bulb temperature (°C)

Absolute humidity (kg/kg’)

●

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.

Pay special attention to extreme operating conditions.

1.1 Cold Weather Area Intermittent Operation

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

U-53

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.

U-54

CHAPTER 5 ● System Design Recommendations

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

Measurement

Air Volume Exhaust Air

Supply Air

Transmission

Max. Workplace

Conditions

Gas Ratio Concentration Concentration Rate

Concentrations

QSA/Q

RA CRA (ppm) CSA (ppm) (%) (ppm)

Hydrogen fluoride 1.0 36 <0.5 - 0 0.6

Hydrogen chloride 1.0 42 <0.5 - 0 5

Nitric acid 1.0 20 <0.5 - 0 10

Sulfuric acid 1.0 2.6 mg/m

3

- 0 mg/m

3

- 0 0.25

Trichlene 1.0 85 2.5 2.9 200

Acetone 1.0 5 0.13 2.5 1,000

Xylene 1.0 110 2.5 2.3 150

Isopropyl alcohol 1.0 2,000 50 2.5 400

Methanol 1.0 41 1.0 2.4 200

Ethanol 1.0 35 1.0 2.9 1,000

Ethyl acetate

1.0 25 0.55 2.2 400

alcohol

Ammonia 1.0 70 2 2.9 50

Hydrogen sulfide 1.0 15 0.44 2.9 10

Carbon monoxide 1.0 71.2 0.7 1.0

Carbon dioxide 1.0 44,500 1,400 1.8

Smoke 1.0 – – 1 - 2

Formaldehyde 1.0 0.5 0.01 2 0.08

Sulfur hexafluoride 1.0 27.1 0.56 2.1

Skatole 1.0 27.1 0.56 2.0

Indole 1.0 27.1 0.56 2.0

Toluene 1.0 6.1 0.14 2.3

Measurement method

• Chemical analysis
with colorimetric
method for
H

2SO4, HCHO

• Ultrasonic method
with

gas

concentration

device

for CO, SF

6

•

Infrared method
with gas
concentration
device for CO

2

•

Gas chromatography
for others

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

Measurement
conditions:

27°C, 65% RH

* OA density for

CO

2 is 600 ppm.

U-55

CHAPTER 5 ● System Design Recommendations

Main Solubility Max.

Generation Gas

Molecular Gas Hazardous

in Water Workplace

Useability

Site

Formula Type level

Concentration

of Lossnay

m /m

g/100g

Sulfuric acid H

2SO4 Mist Toxic 2,380 0.25

×

Nitric acid HNO

3 Mist Toxic 180 10

×

Phosphoric acid H

3PO4 Mist Toxic 41 0.1

×

Acetic acid CH

3COOH Mist Bad odor 2,115 25

×

Chemical

Hydrogen chloride HCl Gas Toxic 427 58 5

×

plant or

Hydrogen fluoride HF Gas Toxic 90 0.6

×

chemical

Sulfur dioxide SO2 Gas Toxic 32.8 0.25

laboratory

Hydrogen sulfide H

2S Gas Toxic 2.3 10

Ammonia NH

3 Gas Bad odor 635 40 50

×

Phosphine PH

3 Gas Toxic 0.26 0.1

Methanol CH

3OH Vapor Toxic Soluble 200

Ethanol CH

3CH2OH Vapor Toxic Soluble 1,000

Ketone Vapor Toxic Soluble 1,000

Skatole C

9H9N Gas Bad odor Minute

Toilet Indole C

9H7N Gas Bad odor Minute

Ammonia NH

3 Gas Bad odor 635 40 50 ×

Nitric monoxide NO 0.0043 50

Others

Ozone O

3 0.00139 0.1

Methane CH

4 0.0301

Chlorine Cl

2 Minute 0.5

Air Mixed gases Gas Non-toxic 0.0167

Air

Oxygen O

2 Gas Non-toxic 0.0283

(reference)

Nitrogen N

2 Gas Non-toxic 0.0143

Carbon monoxide CO Gas Toxic 0.0214

Carbon dioxide CO

2 Gas Non-toxic 0.759

RR

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

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 treated paper of total energy recovery units.

: Recommended : Not recommend ×: Avoid

U-56

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 Mr. Slim indoor units.)

U-57

CHAPTER 5 ● System Design Recommendations

To p

Bottom

Bottom

To p

10. Alternate Installation for Lossnay

10.1 Top/bottom Reverse Installation

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

10.2 Vertical Installation Patterns

Vertical installation is possible, but the installation pattern is limited for some models. Refer to the examples shown for
installation patterns.

Precautions

●

When constructing for vertical installation, make sure that rain water will not enter the Lossnay unit from outdoors.

●

Always transport the unit in the specified state. Vertical installation applies only to after installation, and does not apply to
transportation. (The motor may be damaged if the unit is transported vertically.)

10.3 Slanted Installation

Slanted installation is not recommended.

Special Note:

The LGH-RX model was originally designed for being embedded in the ceiling. Vertical installation is not normally desirable for
installation and maintenance.

SA RA

OA EA

EA OA

RA SA

SA

RA

OA

EA

SA

RA

OA

EA

LGH-15RX5-E
LGH-25RX5-E

Model name Instalattion patterns

LGH-35RX

5-E

LGH-50RX5-E
LGH-65RX5-E
LGH-80RX5-E
LGH-100RX5-E
LGH-150RX5-E
LGH-200RX5-E

To p

Bottom

To p

Bottom

To p

Bottom

To p

Bottom

U-58

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.

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 generating component Additional fan

EA

OA

Lossnay

Lossnay fan

SA RA

H

H

1

H

H

1

H2

H1 + H

2

Q

1

Q1 Q1’

Lossnay with static pressure
increasing component.

Lossnay with static pressure
increasing component.

Lossnay without static
pressure increasing
component.

Q

(Air volume) (Air volume)

Q

A

Lossnay
specification
curve

Lossnay
specification
curve

(Static pressure) (Static pressure)

Lossnay with
extra fan

Extra fan
specification
curve

CHAPTER 6

Examples of Lossnay Applications

U-60

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 floor 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 specifications

: Basement floor SRC (Slab Reinforced Concrete), seven floors above ground floor

Total floor space 30,350 m

2

●

Basement : Employee cafeteria

●

Ground floor : Lobby, conference room

●

2nd to 7th floor : Offices, salons, board room

●

Air conditioning system

: Package air conditioning

●

Ventilation : Ceiling embedded-type Lossnay, straight centrifugal fan

1.2 System Requirements

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

●

Free independent operation system

●

Simple control

(2) Effective use of floor space

(Eliminating the equipment room)

(3) Application to Building Management Laws

●

Effective humidification

●

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

Grille

SA (Supply air)

Indoor unit of
air conditioner

Indoor unit of
air conditioner

Supply grille

RA (Return air)

SA (Supply air to room)

EA
(Exhaust
air)

OA
(Outdoor
air
suction)

EA
(Exhaust
air)

OA
(Outdoor
air
suction)

Suspension bolt
position

Suspension bolt

Inspection

space

Lossnay

Lossnay

Inspection

hole

Inspection hole

U-61

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)

SA (Supply air)

RA (Return air)

Discharge grille

Discharge grille

Suspension bolt
position

Suspension bolt

Suspension bolt
position

Inspection

space

Lossnay

Lossnay

EA
(Exhaust air)

OA
(Outdoor
air suction)

EA
(Exhaust air)

OA
(Outdoor air suction)

Inspection

hole

Inspection hole

U-62

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 floor indoor units of air conditioner system layout

= Lossnay A Air-cooling heat pump air conditioner

B Air-cooling heat pump air conditioner

Additional room

Additional room

Women's
dressing room

Additional
rooms

Machine
room

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

Office

Office

U-63

CHAPTER 6 ● Examples of Lossnay Applications

(3) Humidification

If the load fluctuation of the required humidification 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 humidification and dust removal; in these terms, it was
recommended that a humidifier was added to the air conditioning system to allow adequate humidification.
Installing of a filter 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 filter 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.

U-64

CHAPTER 6 ● Examples of Lossnay Applications

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 Humidification was possible by adding a humidifier.

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

●

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

●

Board room Lossnay in each room.

●

Toilet, powder room

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

●

Kitchenette

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

●

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

the building was surrounded by

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

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 flow must be considered for the entire floor and the ventilator was installed in the ceiling plenum.

System Design

●

Application : Office

●

Building specification: RC (Reinforced Concrete)

●

Total floor space : 552 m2(B1 to 5F)

●

Application per floor : B1: Parking area

GF to 5F: Office

●

Air conditioning system

: Package air conditioner

●

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. (Generally,

only “Class 3” ventilation (forced exhaust) was possible.)

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

could have affected air quality.

(4) Humidification during winter was not possible.

}

}

}

GF Layout 1F to 5F Layout

PAC: Package air conditioner
LS : Lossnay

U-65

CHAPTER 6 ● Examples of Lossnay Applications

2.4 Outcome

(1) Appropriate ventilation was possible with “Class 1” ventilation (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 infiltrating into other rooms was prevented with constant ventilation using an adequate ventilation air volume.

(4) Humidification 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 “Class 1” ventilation (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 specification

: RC (Reinforced Concrete)

●

Total floor space : 931 m2(GF to 2F)

●

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

1F : Patient rooms, nurse station, rehabilitation room, cafeteria
2F : Patient rooms, nurse station, head nurse room, office

●

Air conditioning system

: Fan coil unit, package air conditioner

●

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

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 infiltrating 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

U-66

CHAPTER 6 ● Examples of Lossnay Applications

Reception

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 LP
Lossnay units, or independent system with ceiling
suspended-type Lossnay units.

●

Surgery theater

Combination of LP Lossnay and package air-conditioner
with HEPA filter 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 extra­high mode (25R, 50R 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 flow 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.

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.

●

Humidification was possible by adding a humidifier.

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

●

Odors infiltrating into other rooms were prevented.

GF Layout

1F Layout

2F Layout

Medicine
supply
storage

Gastro
camera
room

X-ray
room

Kitchen

Surgery

theater

Machine
room

Director
room

Inspection
room

Diagnosis
room

Pharmacy

Storage

Waiting
room

Lossnay

Foyer

Prep
room

Nurse
beds

Nurse

station

Patient

room

(1 bed)

Patient

room

(1 bed)

Patient

room

(1 bed)

Patient

room

(4 beds)

Cafeteria/

lounge

Lossnay

Lossnay

Storage

Patient

room

(4 beds)

Patient

room

(4 beds)

Rehabilitation

room

Kitchenette

Storage/
machine

room

Conference

room

Patient

room

(1 bed)

Patient

room

(1 bed)

Patient

room

(1 bed)

Patient

room

(1 bed)

Patient

room

(1 bed)

Patient

room

(1 bed)

Patient

room

(1 bed)

Patient

room

(1 bed)

Storage

Patient

room

(2 beds)

Nurse
beds

Nurse

station

Head

nurse

room

Office

Treatment
room

U-67

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 floor space : 23,000 m

2

●

Building specifications

: Prep school (high school wing)

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.

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 soundproofing was realised.

4.4

Criteria for installing air conditioning

system in schools (Example)

(1) Zoning according to application must be possible.

(2) Response to load fluctuations must be swift.

(3) Ventilation properties must be ideal.

(4) The system must be safe and firmly installed.

(5) Future facility expansion must be easy.

(6) Installation in existing buildings must be possible.

(7) Installation and maintenance costs must be low.

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 proofing, 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) “Class 1” ventilation was applied, and the total energy recovery unit was mainly used in consideration of the energy saved

during air conditioning and the high soundproofing properties.

Classroom Layout

(Hallway) SA RA

RA

RA

RA

RA

SA

SA

RA

SA

SASA

OA EA OA

(Veranda)

RA

LS LS

SA SA

SA

(Classroom)

U-68

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
fluctuations 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 30 m

3

/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 CO

2

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 fluctuations 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.

Conference Room Ventilation System Diagram

Convention and Banquet Hall Ventilation System Diagram

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

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

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-69

CHAPTER 6 ● Examples of Lossnay Applications

6.

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 specifications

:Two floors above ground floor, Total floor space: 385 m

2

●

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

1F

. . . . .

Meeting room

●

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

1F

. . . . .

Air-cooling heat pump package air conditioner

●

Ventilation : Ceiling-embedded Lossnay unit

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 soundproofing 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 1F Layout

Machine room

Kitchenette

Stairway

Toilet

Hall

Foyer

Study room

Day-care room

FCU

FCU

FCU

Lounge

Study room

Meeting room

LS

PAC

PAC

LS

LS

LS

CHAPTER 7

Installation Considerations

U-72

CHAPTER 7 ● Installation Considerations

●

Always leave inspection holes ( 450 or 600) on the
air filter 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.

1. LGH-Series Lossnay Ceiling Embedded-Type
(LGH-RX

5 Series)

LGH-15 · 25 · 35 · 50 · 65 · 80 · 100RX

5 models

●

Always leave inspection holes ( 450 or 600) on the
air filter 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.

LGH-150 · 200RX

5

■ Installation diagram

■ Installation diagram

Duct

Duct

Duct diameter 250
(user supplied)

Duct
diameter 200

(user supplied)

(user supplied)

Exhaust grille
(user supplied)

(user supplied)

(user supplied)

(user supplied)

Ceiling suspension
bolt

450( 600) Inspection port

(user
supplied)

Y piping,Dwindle pipe

Ceiling suspension
bolt position

Ceiling
suspension

bolt position

Exhaust grille

Ceiling
suspension
bolt position

SA

(supply air)

RA

(return air)

OA

(fresh-air intake)

EA

(exhaust-air outlet)

OA

(fresh-air intake)

EA

(exhaust-air outlet)

Heat exchanger/filter
maintenance space

Min. 600

150~250

B

A

SA

(supply air)

Air-supply grille

Exhaust grille

RA

(return air)

Duct incline
Over 1/30
(toward the wall)

to prevent entry
of rainwater

Air-supply grille
(user supplied)

(user supplied)

Air-supply grille

Air-supply grille

450( 600)

Inspection port

(user supplied)

(user supplied)

A

OA

(Outside air)

EA

(Exhaust air)

OA (Outside air)

EA (Exhaust air)

414

414

Suspension bolt position

Suspension bolt position

Suspension bolt
position

Exhaust air grille

B

Supply air grille

600 or more

150 to 250

Inspection

opening

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

Deep-type hood or
weather cover

Duct diameter ¿200
(ordered by customer)

Inspection opening

Supply/
exhaust air grille

Suspension bolt position
(ordered by customer)

RA

(Return air)

SA
(Supply air)

Lossnay Core/
air filter/
fan maintenance
space

(Rainwater entrance
prevention)

Air volume (m3/h) Model

Dimension

AB

150 LGH-15RX

5 768 782

250 LGH-25RX

5 768 782

350 LGH-35RX

5 875 921

500 LGH-50RX

5 875 1,063

650 LGH-65RX

5 895 1,001

800 LGH-80RX

5 1,010 1,036

1000 LGH-100RX

5 1,010 1,263

Air volume (m3/h) Model

Dimension

AB

1500 LGH-150RX

5 1,010 1,045

2000 LGH-200RX

5 1,010 1,272

Unit (mm)

Unit (mm)

material

Heating-insulation

Taping

Heating-insulation
material

Duct connecting flange

Taping

Duct

Should secure with airtight
tape to prevent air leakage.

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

●

Ducting
Indoor Outdoor

EA
(exhaust
air outlet)

OA
(outside
air intake)

EA
(exhaust
air outlet)

OA
(outside
air intake)

Lossnay unit

Electrically operated damper
(Protection against the intrusion of cold air

while Lossnay is stopped in winter)

(To be provided by the customer)

●

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.

U-73

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

OA

EA



OA

EA

OA

EA

*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 (a square, 450 mm each side) to access the filter 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 RX

5-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.)

(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.

EA

SA SA

RA RA

OA EA

Reversed
installation

Lossnay Lossnay

Inspection

opening

Standard
installation

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

Return grille

Exhaust
Air intake

Air intake

Ceiling embedded­type Lossnay unit

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

Return grille

Ceiling

Ceiling

Exhaust

Ceiling embedded­type Lossnay unit

CHAPTER 8

Filters

U-76

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 filters

Aerosol particle diameter (µm)

Solid
particles

Fumes Dust

Mist

Clay

Oil fumes

Tobacco smoke

Carbon black

ZnO fumes

Sea salt

particles

Atmospheric

dust

Fine dust, coarse
dust filters

Cement

Pollen

Viruses

Bacteria

Hair

Medium to high efficiency filters

HEPA filter

Coal dust

Fry ashes

Mud Sand

Sprays

Fluid
particles

Air filters

Major
particles

Aerosol particle

0.001 0.01 0.1 0.3 1 10 100 1000

Table 2. Dust Concentrations

Type Reference Data

Outdoor air dust

Large city 0.1 - 0.15 mg/m

3

concentration

Small city 0.1 mg/m

3

or less

Industrial districts 0.2 mg/m

3

or more

General office 10 mg/h per person

Indoor dust concentration Stores 5 mg/h per person

Applications with no tobacco smoke 5 mg/h per person

Remarks:

1. Outdoor dust is said to have a diameter of 2.1 µm; the 11 types of dust (average diameter 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 0.72 µm. The 14 types of dust (average

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. 4 cm

Amount of dust generated by one cigarette : Approx. 10 mg/cigarette

U-77

CHAPTER 8 ● Filters

Tes ted

dust

Measurement

method

Filter type

Applicable

model

Commercial
Lossnay (LGH)

Optional Part for
model
LGH-15RX

5 -

200RX5

Protection of heat
recovery element

Assurance of sanitary
environment
(According to Building
Management Law)

AFI

Gravitational

method

Compound

dust

ASHRAE

Colorimetric

method

Certificate

in EU

Atomspheric

dust

Countingh method

(DOP method)

Application

JIS 14 types
DOP 0.8 µm

DOP 0.3 µm

82% 8% - 12% G3 (EU3) 5% - 9% 2% - 5%

99% 65% F7 (EU7) 60% 25%

Pre-filter NP/400

High Model
efficiency PZ-15RFM ­filter 100RFM

3.

Calculation Table for Dust Collection Efficiency of Each Lossnay Filter

3.1 High-Efficiency Filter (Optional Parts)

A

B

25

AIR

FLOW

Model

PZ-15RFM-E PZ-25RFM-E PZ-35RFM-E PZ-50RFM-E PZ-65RFM-E PZ-80RFM-E

PZ-100RFM-E

LGH-15RX

5

-E
LGH-35RX

5

-E LGH-50RX

5

-E LGH-65RX

5

-E

LGH-80RX5-E

LGH-100RX5-E

LGH-25RX5-E

LGH-150RX

5

-E LGH-200RX5-E

A 553 327 393 464 427 446 559

B119 144 171 171 205 232 232

Number of filters perset 1222222

Note: This is one set per main body.

PZ-15RFM-E

100

50 100 150 200 250

50

0

Air volume (m

3

/h)

Pressure Loss (Pa)

PZ-25RFM-E

100

100 200 300 400

50

0

Air volume (m

3

/h)

Pressure Loss (Pa)

PZ-35RFM-E

100

100 200 300 400 500

50

0

Air volume (m

3

/h)

Pressure Loss (Pa)

PZ-65RFM-E

200 400 600 800

100

50

0

Air volume (m

3

/h)

Pressure Loss (Pa)

PZ-50RFM-E

100

200 400 600

50

0

Air volume (m

3

/h)

Pressure Loss (Pa)

PZ-80RFM-E

100

200 400 600 800 1000

50

0

Air volume (m

3

/h)

Pressure Loss (Pa)

PZ-100RFM-E

200 400 600 800 1000 1200

Air volume (m

3

/h)

100

50

0

Pressure Loss (Pa)

3.2 Pressure Loss

■ Pressure Loss Characteristics

Dimension(mm)

(2sets) (2sets)

Applicable Model

U-78

CHAPTER 8 ● Filters

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

20

40

60

80

100

Collection ratio (%)

High efficiency
filter

Colourimetric method
90% filter

NP/400

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

20 30

40 60 80 100

Particle diameter (µm)

U-79

CHAPTER 8 ● Filters

Test Method Test Dust

Inward Flow Dust Outward Flow Dust Efficiency

Type of Applicable

Measurement Method Measurement Method Indication Method

Filters

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

road in Arizona: 72%

measured • Weigh the dust Gravitational ratio Synthetic dust filters

method •

K-1 carbon black: 25%

beforehand remaining on the

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

NBS Degree of Degree of Comparison of Electrostatic dust
Colorimetric Atmospheric dust contamination of contamination of contamination of percentage of
method white filter paper white filter paper reduction in degree (for air conditioning)

of contamination

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

Synthetic: • Filter passage air Pre-filter
ASHRAE •

Regulated air cleaner

Dust weight volume measured Filter for air
Gravitational fine particles: 72% measured • Weigh the dust Gravitational ratio conditioning
method •

Morocco Black: 23%

beforehand remaining on the (for coarse dust)

• Cotton linter: 5% filter and compare

ASHRAE Degree of Degree of Comparison of Filter for air
Colorimetric Atmospheric dust contamination of contamination of percentage of conditioning (for fine
method white filter paper white filter paper reduction in degree dust) Electrostatic

of contamination dust collector

Air filter test for air

Comparison of

conditioning set by Degree of Degree of

percentage of Filter for air

Japan Air Cleaning JIS 11-type dust contamination of contamination of

reduction in degree conditioning

Assoc. white filter paper white filter paper

of contamination

(Colorimetric test)

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

Electrostatic air

Comparison of

cleaning device test Degree of Degree of

percentage of Electrostatic dust

set by Japan Air JIS 11-type dust contamination of contamination of

reduction in degree collector

Cleaning Assoc. white filter paper white filter paper

of contamination

(Colorimetric test)

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.

U-80

CHAPTER 8 ● Filters

Gravitational Method

This method is used for air filters that remove coarse dust (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

× 100 (%)

In-flow side dust amount

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 =

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

× 100 (%)

Out-flow side sampling amount

Orifice

Dust supply
device

Manometer

Motor

Dust container

Mixing blades

Dust supply outlet

Unit (mm)

Rectifying grid

Air volume
adjustment plate

Air-feed fan

Window

Specimen

Performance test device Example of dust supply device

Dust collection filter

Air-feed fan

Orifice

Square duct

Throttle device

Rectifying grid

Venturi pipe

Dust chamber

Air filter

Specimen

3.5D3D 2D 2L 2L

Baffle plate

Coupling pipe

7° or
less

Pressure loss concentration
measurement position

Coupling pipe

Rectifying grid

Coupling

pipe

Round duct

U-81

CHAPTER 8 ● Filters

When the performance of each machine is known, the indoor dust concentration Ci

may be obtained with the filter

performance, η

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

C

i

=

G + C

o Q

o (1 – η

o)

Q

o

+ Qi

ηi

Also, with the value of Ci and ηo known, indoor unit of air conditioner efficiency can be found using:

η

i =

G + Co Qo (1 – ηo) – Ci Qo

× 100

C

i Qi

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

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

i :

Indoor unit of air conditioner air volume
(Total air volume of indoor unit) (m

3

/h)

ηo : Filtering efficiency of humidifier with high efficiency filter %

(colorimetric method)

η

i : Efficiency of the filter for the indoor unit of air conditioner %

(colorimetric method)

C

o : Outdoor air dust concentration (mg/m

3

)

C

i : Indoor dust concentration (mg/m

3

)

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

Indoor unit of air conditioner

Lossnay unit

High-efficiency filter ηo

Indoor unit filter ηi

6. Certificate in EU

Pre-filter of LGH-RX5 series are certificated as G3(EU3), and High-efficiency filter of model PZ-15-100RFM are certificated as
F7(EU7) under BS EN779 : 1993 / Eurovent 4/5 Filter Test.

Certificate No. C18070A/3 Certificate No. C18070B/2

CHAPTER 9

Service Life and Maintenance

U-84

CHAPTER 9 ● Service Life and Maintenance

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-filter

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.)

Models LGH-15 to 100RX5 Models LGH-150 and 200RX5

Hinge

Hinge
bracket

Maintenance cover

Maintenance cover

Hinge

Lossnay core

Handle

Handle

Lossnay
core

Models LGH-15 to 100RX5 Models LGH-150 and 200RX5

Main unit

Hinge
bracket

Air filter

Main unit

Air filter

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.

Models LGH-15 to 100 RX

5: ..................................... 4 filters

Models LGH-150 and 200 RX

5: ................................ 8 filters

CAUTION

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

Take filter stoppers careful not to break them.

2) Lossnay cores

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

Models LGH-15 to 100 RX5: ..................................... 2 cores

Models LGH-150 and 200 RX

5: ................................ 4 cores

2.1 Removing the parts

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.

Filter stopper

Filter guide

U-85

CHAPTER 9 ● Service Life and Maintenance

Vacuum cleaner

Air filter

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.

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.
The filter for LGH-35RX5 has front and back side. Set the “FRONT”
(printed) side of the filter on the outer side.

Note

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

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.

Do NOT wash in water.

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 40 C)

Corner

Vacuum cleaner
(with brushi attachment)

Lossnay core

CHAPTER 10

Ventilation Standards in Each Country

Room Environment Standard Values

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

Central air quality management system ventilation
capacity and characteristics

Effective ventilation capacity V 20Af/N(m

3

)

Af: Floor space (m2); N: Floor space occupied by one person

For general ventilation, the effective ventilation area
opening is at least 1/20 of the floor space, and the
ventilation equipment installed gives a CO density of
50 ppm and CO

2 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.

U-88

CHAPTER 10 ● Ventilation Standards in Each Country

1. Ventilation Standards in Each Country

1.1 Japan

Summary of Laws Related to Ventilation

Item

Related Laws

Law for Maintenance
of Sanitation in
Buildings

The Building
Standard Law of
Japan

Industrial Safety and
Health Act

Acceptable Range

Buildings of at least
3,000 m

2

(for schools, at

least 8,000 m

2

).

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 fire.

Offices.
(Office sanitation
regulated standards)

Remarks

Applicable buildings are
those designed to serve a
specific purpose.

Applicable buildings are
those with ventilation
equipment requirements.

Impurity Volume of Less than 0.15 mg per 1 m

3

Particles of air

Less than 10 ppm. (Less than 20

CO Rate

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

CO

2 Rate Less than 1,000 ppm.

1) Between 17°C and 28°C

2)

When making the room

Temperature

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

Relative Humidity 40% - 70%

Ventilation Less than 0.5 m/sec.

Impurity Volume of Less than 0.15 mg per 1 m

3

Particles of air

CO Rate Less than 10 ppm.

CO

2

Rate Less than 1,000 ppm.

1) Between 17°C and 28°C

2)

When making the room

Temperature

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

Relative Humidity 40% - 70%

Ventilation Less than 0.5 m/sec.

Impurity Volume of

Air (1 atmospheric pressure, 25°C)

Particles

less than 0.15 mg per 1 m3of air

Less than 10 ppm. (Less than 20 ppm

CO Rate

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

CO2 Rate Less than 1,000 ppm.

Air flow in room is less than

Air Flow

0.5 m/s, and air taken into the room
does not blow directly on or reach
occupants.

Heat and Humidity Heat between 17°C - 28°C

Conditions Relative humidity 40% - 70%

U-89

CHAPTER 10 ● Ventilation Standards in Each Country

2. United States of America

ASHRAE Standard 62 - 2001

3. United Kingdom

CIBSE

Outdoor air

Application Recommended Minimum Smoking

Per person Per person Per m

2

Factories 8 l/s /person 5 l/s /person 0.8 l/s / m

2

None

Offices (open plan) 8 l/s /person 5 l/s /person 1.3 l/s / m

2

Some

Shops, department stores, and supermarkets

8 l/s /person 5 l/s /person 3.0 l/s / m

2

Some

Theaters 8 l/s /person 5 l/s /person — Some

Dance halls 12 l/s /person 8 l/s /person — Some

Hotel bedrooms 12 l/s /person 8 l/s /person 1.7 l/s / m

2

Heavy

Laboratories 12 l/s /person 8 l/s /person — Some

Offices (private) 12 l/s /person 8 l/s /person 1.3 l/s / m

2

Heavy

Residences (average) 12 l/s /person 8 l/s /person — Heavy

Restaurant (cafeteria) 12 l/s /person 8 l/s /person — Heavy

Cocktail bars 18 l/s /person 12 l/s /person — Heavy

Conference rooms (average) 18 l/s /person 12 l/s /person — Some

Residence 18 l/s /person 12 l/s /person — Heavy

Restaurant 18 l/s /person 12 l/s /person — Heavy

Board rooms, executive offices, and

25 l/s /person 18 l/s /person 6.0 l/s / m

2

Very

conference rooms Heavy

Corridors N/A N/A 1.3 l/s / m

2

N/A

Kitchens (domestic) N/A N/A 10.0 l/s / m

2

N/A

Kitchens (restaurant) N/A N/A 20.0 l/s / m

2

N/A

Toilets N/A N/A 10.0 l/s / m

2

N/A

Estimated Maximum*

Application Outdoor Air Requiremen

ts Occupancy

P/1000 ft

2

or 100 m

2

Commercial dry cleaner 30 cfm/person 30

Dining rooms 20 cfm/person 70

Bars, cocktail lounges 30 cfm/person 100

Kitchens (cooking) 15 cfm/person 20

Hotel bedrooms 30 cfm/room —

Hotel living rooms 30 cfm/room —

Hotel lobbies 15 cfm/person 30

Gambling casinos 30 cfm/person 120

Office space 20 cfm/person 7

Conference room 20 cfm/person 50

Smoking lounge 60 cfm/person 70

* Net occupiable space.

CHAPTER 11

Lossnay Q and A

U-92

CHAPTER 11 ● Lossnay Q and A

Question Answer Remarks

Paper is used for the
material, but does it have an
adequate life span?

Is the paper an insulation
material? (Poor conductor of
heat)

If the paper can recover
humidity, will it not become
wet?

When is the forced

4

simultaneous air intake/
exhaust-type more
efficient?

What are the energy

5 conservation properties of

Lossnay units?

The cellulose membrane will last an adequate amount of time unless it is
intentionally damaged, placed in water or in direct sunlight (ultra-violet
rays). The life is longer than metal as it does not rust.

The cellulose membrane is very thin, and thus the conductivity of the
material is low, with heat being transferred approximately the same as
metal. This can be tested placing a piece of paper between hands and
feel the warmth of the palms. The recovery of humidity can also be felt by
blowing on the paper and feeling the moisture in the breath being
transferred to the palm.

It is similar to the phenomenon during heating in winter where the window
pane is wet but the paper blinds are dry - humidity is transferred through
the paper membrane.

When a building is sealed and normal ventilation is used, accurate
exhaust is not possible unless a suction inlet is created.
Lossnay units have both an air-supply fan and air-exhaust fan so “Class
1” ventilation is possible.

For an example, in an approx. 13 m

2

room with five people, a ventilation

volume of 100 m

3

/h is required. The amount of power consumed in this
case is approximately 45 W, and the amount of energy recovered during
cooling is approximately 700 W or more. The coefficient of performance
(C.O.P.) obtained when converted with the unit power generation amount
is 16. When compared to a popular heat pump has a C.O.P. of 2 to 3, the
Lossnay can serve a high amount of energy.
If a general-purpose ventilator is installed, the cooled air will be lost, thus
increasing electrical costs throughout the year.

Depending on
conditions, the
cellulose membrane
can be stored for up to
2,000 years without
deteriorating.

1

2

3