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Mitsubishi
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LGH 15-200RX4
Service Manual [eng]
77 pgs11.05 Mb0
TECHNICAL MANUAL
220 pgs5.88 Mb0
Table of contents
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Mitsubishi LGH-15...200RX4, RX4 TECHNICAL MANUAL

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Page 1
 
Page 2
Page 3

Lossnay Unit

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i

CONTENTS

CHAPTER 1 Ventilation for Healthy Living
1. Necessity of Ventilation ...................................................................................................................................... 2
4. Ventilation Performance ...................................................................................................................................... 8
5. Outdoor Air (ventilation) Load .............................................................................................................................. 10
CHAPTER 2 Lossnay Construction and Principle
1. Construction and Features of Lossnay .............................................................................................................. 16
2. Construction and Principle of Core ...................................................................................................................... 16
3. Calculation of the Total Heat Recovery Efficiency .............................................................................................. 18
4. What is a Psychrometric Chart? ........................................................................................................................ 19
5. Calculation of Lossnay Heat Recovery .............................................................................................................. 20
CHAPTER 3 General Technical Considerations
1. Lossnay Heat Recovery Effect ............................................................................................................................ 22
2. Example Heat Recovery Calculation .................................................................................................................. 24
3. Calculation of Lossnay Economical Effects ........................................................................................................ 26
4. Psychrometric Chart .......................................................................................................................................... 28
5. The Result of No Virus (phage) Cross Contamination for the Lossnay Core and Determining
Resistance of the Lossnay Core to Molds .......................................................................................................... 29
6. Flame-proofing Properties of Lossnay Core ...................................................................................................... 31
7. Lossnay Core’s Soundproofing Properties Test .................................................................................................. 33
8. Change in Lossnay Core Over Time .................................................................................................................. 34
9. Comparison of Heat Recovery Techniques ........................................................................................................ 36
CHAPTER 4 Characteristics
1. How to Read the LGH Series Lossnay Characteristic Curves ............................................................................ 40
2. Calculating the Static Pressure Loss .................................................................................................................. 40
3. How to Obtain Efficiency from Characteristic Curves ........................................................................................ 44
4. Sound .................................................................................................................................................................. 45
5. NC Curves (LGH-RX
4 Series) ............................................................................................................................ 51
CHAPTER 5 System Design Recommendations
1. Lossnay Usage Conditions ................................................................................................................................ 58
2. Noise Value of Lossnay with Built-in Fans .......................................................................................................... 59
3. Attachment of Air Filter ...................................................................................................................................... 59
6. Transmission Rate of Various Gases and Related Maximum Workplace Concentration .................................. 60
7. Solubility of Odors and Toxic Gases, etc., in Water and Effect on Lossnay Core .............................................. 61
8. Positioning of the Supply/Exhaust Fans and the Air Transmission Rate
(excluding moisture resistant total heat recovery units) ...................................................................................... 62
9. Combined Operation with other Air Conditioners ................................................................................................ 63
10. Automatic Ventilation Switching .......................................................................................................................... 64
11.Vertical Installation of LGH Series ...................................................................................................................... 65
12. Installation of Supplementary Fan Devices After Lossnay Unit .......................................................................... 66
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CHAPTER 6 Examples of Lossnay Applications
2. Medium Size Office Building .............................................................................................................................. 71
3. Multipurpose Tenant Building .............................................................................................................................. 74
4. Urban Small-Scale Building ................................................................................................................................ 77
5. Hospitals ............................................................................................................................................................ 78
6. Schools .............................................................................................................................................................. 80
7. Hotels (convention halls, wedding halls) ............................................................................................................ 82
8. Public Halls (combination facilities such as day-care centres) .......................................................................... 85
CHAPTER 7 Installation Considerations
1. LGH-Series Lossnay Ceiling Embedded-Type (LGH-RX
4 Series) ...................................................................... 86
2. Building Lossnay Unit Horizontal-type (LU-500) ................................................................................................ 89
CHAPTER 8 Filtering for Freshness
2. Data Regarding Dust .......................................................................................................................................... 92
3. Calculation Table for Dust Collection Efficiency of Each Lossnay Filter ............................................................ 93
4. Comparison of Dust Collection Efficiency Measurement Methods .................................................................... 95
5. Calculation of Dust Concentration ...................................................................................................................... 97
CHAPTER 9 Service Life and Maintenance
2. Cleaning the Lossnay Core and Pre-filter .......................................................................................................... 100
CHAPTER 10 Ventilation Standards in Each Country
1. Ventilation Standards in Each Country ................................................................................................................ 102
2. U.S. ...................................................................................................................................................................... 103
3. U.K....................................................................................................................................................................... 103
CHAPTER 11 Lossnay Q and A .......................................................................................................................... 106
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CHAPTER 1
Ventilation for Healthy Living

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CHAPTER 1 ● Ventilation for Healthy Living
Fresh outdoor air must be introduced constantly at a set ratio in an air conditioning system. This fresh air is introduced to be mixed with the return air from the room, to adjust the temperature and humidity, supply oxygen, reduce body and other odors, remove tobacco smoke and to increase the cleanness of the air. The standard ventilation (outdoor air intake) volume is determined according to the type of application, estimated number of persons in the room, room area, and relevant regulations. Systems which accurately facilitate these requirements are increasingly being required to be installed in buildings.

1. Necessity of Ventilation

The purpose of ventilation is basically divided into “oxygen supply”, “cleaning of air”, “temperature control” and “humidity control”. Cleaning of the air includes the elimination of “odors”, “gases”, “dust” and “bacteria”. The needs of ventilation are divided into “personal comfort”, “assurance of environment for animals and plants”, and “assurance of environments for machinery and constructed materials”. In Japan legal regulations regarding ventilation are set in the Building Srandard Law Enforcement Ordinance and the “Building Management Law” for securing a sanitary environment in buildings. These are in general agreeance with similar regulations in other countries.
1.1 Room air environment in buildings
In Japan, the Building Management Law, a law concerning the sanitary environment of buildings, designates eleven applications including offices, shops, and schools with a total floor area of 3,000 m
2
or more, as buildings. According to this law maintenance and management of the ventilation and water supply and discharge 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 5,000 m
2
in particular areas.
The ratio of 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 is shown in the chart at the right.
There was a large decrease in unsuitable percentages of floating particles, but there was almost no change in temperature and carbon dioxide. Values for temperature, ventilation, and carbon monoxide almost entirely cleared the standard values, and are excluded. The study from 2002 shows the item with the highest percentage of unsuitability as temperature with 2.7%, followed by carbon dioxide at 22.8%.
70
60
50
40
30
20
10
0
Percentage of unsuitability (%)
76 77 78 79 80 8171 72 73 74 75
82
83 84
85
86
87
88 899091 92 93 94 95 96 97 98 99 00 01 02
(year)
relative humidity
carbon dioxide
temperature
carbon monoxide
ventilation
floating particles (tobacco smoke)
Percentage of unsiutability of air quality by year
(From reference data in the 2003 edition of the “Water Supply
Division, Dept. of Localized PublicHealth, 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
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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.
5 Considered to be the long-term tolerable value.
10
The Building Standard Law of Japan, Law for Maintenance of Sanitation in Buildings. Environmental standard 24-hour average.
20
Considered to be the short-term tolerable value. Environmental standard 8-hour average.
50
Tolerable concentration for labor environment. (Japan Industrial Sanitation Association)
100
No effect for 3 hours. Effect noticed after 6 hours. Headache, illness after 9 hours; harmful for long-term but not fatal.
200 Light headache in the forehead in 2 to 3 hours.
400 Headache in the forehead, nausea in 1 to 2 hours; headache in the back of head in 2.5 to 3 hours.
800 Headache, dizziness, nausea, convulsions in 45 minutes. Comatose in 2 hours.
1,600 Headache, dizziness in 20 minutes. Death in 2 hours.
3,200 Headache, dizziness in 5 to 10 minutes. Death in 30 minutes.
6,400 Death in 10 to 15 minutes.
12,800 Death in 1 to 3 minutes.
Several 10,000 ppm
This level may be found in automobile exhaust.
(Several %)
Apprpx. 5 ppm is an annual average value in city areas. 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 will be a guideline where concentration does not decrease more than 0.5% from normal value. (The Building Standard Law of Japan)
20 - 19
An oxygen deficiency of this amount does not directly endanger life in a normal air pressure, but if there is a combustion device in the area, the generation of CO will increase rapidly due to incomplete combustion.
18 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 Threat to life in short term.
7 Fatal
In the case of Japan, an Instruction Guideline based on these regulations has been issued, and unified guidance is carried out. Part of the Instruction Guideline regarding ventilation is shown below.
●
The fresh outdoor air intake must be 10 m or higher from ground level, and be distanced appropriately from the exhaust air outlet. (Neighbouring buildings must also be considered.)
●
The fresh outdoor air intake volume must be 25 to 30 m3/h·person in design.
●
An air volume measurement hole must be installed at an effective position to measure the treated air volume of the ventilating device.
●
The position and shape of the supply diffuser and return grille must be selected so the air environment in the room is distributed evenly.
1.2 Effect of air contamination on human bodies
Effect of oxygen (O2
) concentration
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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 in one to two years. This is caused by dust and the tar in tobacco smoke.

2. Ventilation Standards

The legal standards for ventilation differ according to each country. Please follow the standards set by the country. In the US, Ashrae revised their standards in 1989 becoming 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 environment in buildings. According to the Building Standards Law, a minimum of
20 m
3
/h per person 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 people stay 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 Observed as relatively poor.
0.5 or more Observed as the poorest.
0.5 Long-term safety limits (U.S. Labor Sanitation) ACGIH, regulation of laborer offices.
2 Depth of breathing and inhalation volume increases 30%.
3Work and physical functions deteriorate, breathing doubles.
4 Normal exhalation concentration.
4 - 5
The respiratory center is stimulated; depth and times of breathing increases. Dangerous if breathed in for a long period. If an O
2 deficiency also occurs, trouble will occur sooner and be more dangerous.
8
When breathed in for 10 minutes, breathing difficulties, redness in the face and headaches will occur. The trouble will worsen when there is also a deficiency of O
2.
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.
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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. Ventilation is composed of “Supply air” and “Exhaust air” functions. These functions are classified according to natural flow or mechanical ventilation using a fan (forced ventilation).
Classification of mechanical ventilation
Classification of ventilation (according to Building Standards Law)
1. Class 1 ventilation
Fresh outdoor air is mechanically brought in and simultaneously the stale air in the room is mechanically discharged.
2. Class 2 ventilation
Fresh outdoor air is mechanically brought in and the exhaust air is discharged from the exhaust air outlet (natural).
3. Class 3 ventilation
The stale air in the room is mechanically discharged and simultaneously fresh outdoor air is mechanically introduced from the supply air diffuser (natural).
Ex. of application
•Ventilation of air conditioned rooms. (buildings, hospitals, etc.)
•Ventilation of room not facing an outer wall. (basement, etc.)
•Ventilation of large room. (office, large conference room, hall, etc.)
• Surgery theatre.
• Clean rooms.
• Foodstuff processing factories.
• Local ventilation in kitchens.
•Ventilation of hot exhaust air from machine room, etc.
•Ventilation of humid exhaust air from indoor pools, bath­rooms, etc.
• General simple ventilation.
System effect
By changing the balance of the supply fan and exhaust fan’s air volumes, the pressure in the room can be balanced freely, and the interrelation with neighboring spaces can be set freely.
As the room is pressurized, the flow of odors and dust, etc., from neighboring areas can be prevented.
The exhaust air is removed from a local position in the room, and dispersion of the stale air can be prevented by applying an entire 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 freely is possible.
•A system which adjusts the temperature and humidity of the supply air diffuser flow to the room environment can be incorporated.
•
The supply and exhaust volume can be set freely according to the changes in conditions.
• The position and shape of the supply air diffuser can be set.
• The temperature and humidity of the supply air diffuser flow can be set accordingly, and dust can be removed as required.
•Effective exhausting of dispersed stale air generation sites is possible from a local exhaust air outlet.
•Ventilation in which the air flow is not felt is possible with the supply air diffuser setting method.
Selection points
• Accurate supply air diffuser can be maintained.
• The room pressure balance can be maintained.
• The supply air diffuser temperature and humidity can be adjusted and dust treatment is possible.
• The pressure is positive.
•
The supply air diffuser temperature and humidity can be adjusted, and dust treatment is possible.
•
The positional relation of the exhaust air outlet to the supply air diffuser is important.
• The room pressure is negative.
• Local exhaust is possible.
•Ventilation without dispersing stale air is possible.
•Ventilation with reduced air flow is possible.
•
The positional relation of the exhaust air outlet to the supply air diffuser is important.
Supply air diffuser
Exhaust fan
Exhaust air outlet
Exhaust fan
Exhaust fan
Stale air
Fresh outdoor 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
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1) System operation with cassette-type air conditioner
2) System operation with ceiling embedded-type air conditioner
3) Independent operation with ceiling suspended-type air conditioner
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CHAPTER 1 ● Ventilation for Healthy Living
3.2 Comparison of ventilation methods
There are two main types of ventilation methods.
Centralized ventilation method
This is mainly used in large buildings, with the fresh outdoor air intake being installed in one machine room. For this method, primary treatment of the fresh outdoor air, such as heat recovery to the intake air and dust removal is performed being distribution to the building by ducts.
Independent zoned ventilation method
This is mainly used in small to medium sized buildings, with areas being ventilated using fresh outdoor air intakes formed of independent ventilation devices. The rate of use of this method has recently increased as independent control is becoming ever more feasible.
Centralized ventilation method Independent zoned ventilation method
Air intake
(fresh out-
door air)
Filters
Air exhaust (stale air)
Cassette-type package air conditioner or fan coil unit
Cassette-type or ceiling suspended-type package air conditioner or fan coil unit
Exhaust grill
Ceiling recessed­type Lossnay
Exhaust air Fresh outdoor air
Finished ceiling
Exhaust air Fresh outdoor air
Finished ceiling
Lossnay
Supply fan
Exhaust
Each unit
Ceiling embedded-type package air conditioner or fan coil unit
Ceiling recessed­type Lossnay
Exhaust grill
Exhaust air Fresh outdoor air
Finished ceiling
Ceiling recessed­type Lossnay
Exhaust grill
Supply grill
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CHAPTER 1 ● Ventilation for Healthy Living
Comparison of centralized ventilation method and independent zoned ventilation method
Centralized ventilation method
The air transfer distance is long thus requiring much fan power.
• Independent equipment room is required.
• Duct space is required.
• Penetration of floors with vertical shaft is not desired in terms of fire prevention.
Generalized per system.
• Design of outer wall is not lost.
• The indoor supply air diffuser and return grille can be selected freely for an appropriate design.
As there are many common-use areas, if the building is a tenant building, an accurate assessment of operating cost is difficult.
• As the usage time setting and ventilation volume control, etc., is performed in a central monitoring room, the user’s needs may not be met appropriately.
•A large amount of ventilation is required even for a few persons.
• An ideal supply air diffuser and return grille position can be selected as the supply air diffuser and return grilles can be laid out freely.
• The only noise in the room is the aerodynamic sound.
• Anti-vibration measures must be taken as the fan in the equipment room is large.
• Centralized management is easy as it can be performed in the equipment room.
• The equipment can be inspected at any time.
• Large as the entire system is affected.
• Immediate inspection can be performed in the equipment room.
Fan power
Installation space
Zoning
Designability
Clarification of costs
Controllability
Comfort
Maintenance and management
Trouble correspondence
Independent zoned ventilation method
As the air transfer distance is short, the fan power is small.
• Independent equipment room is not required.
• Piping space is required only above the ceiling.
Can be utilised for any one area.
• The number of intakes and exhaust air outlets on the outer wall will increase; design must be considered.
• The design will be fixed due to the installation fittings, so the design of the intakes and exhaust air outlets must be considered.
Invoicing for each zone separately is possible, even in a tenant building.
• The user in each zone can operate the ventilator freely.
• The ventilator can be operated even during off­peak hours.
• Consideration must be made of the noise from the main unit.
• Anti-vibration measures are often not required as the unit is compact and the vibration generated can be dispersed.
•Work efficiency is poor as the equipment is not centrally located.
• An individual unit can be inspected only when the room it serves is vacant.
• Limited as only independent units are affected.
• Consultation with the tenant is required prior to inspection of an individual unit.
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CHAPTER 1 ● Ventilation for Healthy Living

4. Ventilation Performance

The ventilation performance is largely affected by the installation conditions. Ample performance may not be achieved unless the model and usage methods are selected according to the conditions. Generally, the ventilation performance is expressed by “Air volume” and “wind pressure (static pressure)”, and these are necessary when considering ventilation.
4.1 Air volume
Air volume expresses the volume of air exhausted (or supplied) by the unit in a given period. Generally, this is expressed as m
3
/hr (hour).
4.2 Wind pressure
When a piece of paper is placed in front of a fan and let go, the piece of paper will be blown away. The force that blows the paper away is called the wind pressure, and this is normally expressed in units of Pa. The wind pressure is divided into the following three types:
4.2.1 Static pressure
This is the force that presses the surroundings when the air is still such as in an automobile tyre or rubber balloon. For example, in a water gun, the hydraulic pressure increases when pressed by a piston, and if there is a small hole, the water sprays out with force. The pressure of this water is equivalent to the static pressure for air. The higher the pressure is, the further the water (air) can be sprayed.
4.2.2 Dynamic pressure
This expresses the speed at which air flows, and can be thought of as the force at which a typhoon presses against a building.
4.2.3 Total pressure
This is the total force that wind has, and is the sum of the static pressure and dynamic pressure.
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CHAPTER 1 ● Ventilation for Healthy Living
4.3 Measurement of the air volume and wind pressure
Mitsubishi measures the machine’s air volume and wind pressure with a device as shown below according to the 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 (A point, the static pressure at this point is called the totally closed pressure) can be obtained. Next, the throttle device is gradually opened, the auxiliary fan is operated, and the middle points (points B, C and D) are obtained. Finally, the throttle device is completely opened, and the auxiliary fan is operated until the static pressure in the chamber reaches 0. The maximum point of the air volume (point E, the air volume at this point is called the fully opened air volume) is obtained. The points are connected as shown below, and are expressed as air volume, static pressure curves (Q-H curve).
Connection
Wind dispersing place
Connection
Rectifying
grid
Rectifying
grid
Supply
Air
(SA)
Chamber
Return
Air
(RA)
Rectifying net
Rectifying
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)
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CHAPTER 1 ● Ventilation for Healthy Living

5. Outdoor Air (ventilation) Load

5.1 How to calculate each approximate load
The outdoor air load can be calculated with the following formula if the required outside air intake volume Q m3/h to be introduced is known:
(Outdoor air load) = γ · Q
F · (iO - iR)
= γ [kg/m
3
] × S [m2] × k × n [person/m2] × Vf [m3/h·person] × (iO - iR): ∆i [kJ/kg]
γ : Specific gravity of air - 1.2 kg/m
3
S:Building’s airconditioned area k:Thermal coefficient; generally 0.7 - 0.8. n:The average population concentration is the inverse of the occupancy area per person. If the number of persons in the
room is unclear, refer to the Floor space per person table below.
Vf : Outdoor air intake volume per person
Refer to the Required outdoor air intake volume per person table below.
i
O : Outdoor air enthalpy - kJ/kg
iR
: Indoor enthalpy - kJ/kg
Floor space per person table (m
2
)
(According to the Japan Federation of Architects and Building Engineers Associations)
Required outdoor air intake volume per person table (m
3
/h·person)
Caution
The application of this table to each type of room should be carefully considered in relation to the degree of smoking in the room.
Office building
Department store, shop
Restaurant
Teatre 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
Degree of smoking
Recommended value Minimum value
Broker’s office
Extremely heavy Newspaper editing room 85 51
Conference room
Quite heavy
Bar
51 42.5
Cabaret
Heavy
Office
25.5
17
Restaurant 20
Light
Shop
25.5 17
Department store
None
Theatre 25.5 17 Hospital room 34 25.5
Page 17
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CHAPTER 1 ● Ventilation for Healthy Living
Cooling load per unit area
When the volume of outdoor air per person is 25 m
3
/h, and the number of persons per 1 m2is 0.2, the cooling load will be
approximately 157.0 W/m
2
.
How these values are determined can be seen as follows:
● Outdoor air load
Air conditions <Standard design air conditions in Tokyo>
Example calculations of determining ventilation load during both cooling and heating are given as follows:
5.2 Ventilation load during cooling (in general office building)
● Classification of cooling load
(a) is the heat infiltrating the room, and often is 30 to 40% of the entire cooling load. (b) is the heat generated in the room. (c) is applies only when reheating is necessary. (d) is the heat generated when outdoor air is mixed into part of the supply air diffuser volume and introduced into the room. The outdoor air is introduced to provide ventilation for the people in the room, and is referred to as the ventilating load.
Typical load values (during cooling)
Type of load Load
Outdoor air load 53.0 W/m
2
Indoor
People 26.4 W/m
2
generated heat
Lighting equipment 30.0 W/m
2
Indoor infiltration heat 47.6 W/m
2
Total 157.0 W/m
2
Conditions: Middle floor of a general office building facing south.
Class
Heat from walls (q
WS)
(a) Indoor infiltration heat Heat from glass
from direct sunlight (qGS) from conduction & convection (qGS)
Accumulated heat load in walls (q
SS)
Generated heat from people
Sensible heat (q
HS)
(b) Indoor generated heat
Latent heat (qHL)
Genarated 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
Indoors 26 °C 50% 18.7 °C 53.2 kJ/kg
When the load per floor area of 1 m2with a ventilation volume of 25 m3/h·person is calculated with the above air conditions, the following is obtained:
Outdoor air (ventilation) load = 1.2 kg/m
3
(Specific gravity of air) × 0.2 persons/m2(no. of persons per 1 m2)
× 25 m
3
/h·person (outdoor air volume) × 31.8 kJ/kg (air enthalpy difference indoors/outdoors) = 190.8 kJ/h·m2(530 W/m2)
The Lossnay recuperates approximately 70% of the exhaust air load and saves on approximately 20% of the total load.
Outdoor air
load 33.8%
53.0 W/m
2
Indoor infiltration heat 30.3%
47.6 W/m
2
Indoor
generated heat
(people, lighting
equipment) 35.9%
56.4 W/m
2
156.5 W/m
2
Page 18
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CHAPTER 1 ● Ventilation for Healthy Living
● Determining internal heat gain
When classifying loads, the internal heat gain (indoor generated heat + indoor infiltration heat) will be the value of the outdoor air load subtracted from the approximate cooling load when it is assumed that there is no reheating load.
(Internal heat gain)
= 157.0 W/m
2
– 53.0 W/m2= 104.0 W/m
2
●
This value of internal heat gain is based on assumptions for typical loads. To determine individual levels of internal heat gain, the following is suggested:
● Indoor generated heat
(1) Heat generated from people
Heat generation design value per person in office
Sensible heat (SH)= 63.0 W·person Latent heat (LH) = 69.0 W·person Total heat (TH) = 132.0 W·person
The heat generated per 1 m
2
of floor space is
(heat generated from people)
= 132.0 W·person × 0.2 person/m
2
= 26.4 W/m
2
(2) Heat generated from electrical equipment (lighting)
The approximate value of the room illuminance and power for lighting for a general office with illuminance of 300 ­350 Lux, is 20 - 30 W/m
2
.
● Indoor infiltration heat
This is the heat that infiltrates into the building from outside. This can be determined by subtracting the amount of heat generated by people and lighting from the internal heat gain. (Indoor infiltration heat)
= 104.0 – (26.4 + 30.0) = 47.6 W/m
2
The Lossnay recuperates approximately 70% of the outdoor air load and saves on approximately 20% of the total load.
Page 19
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CHAPTER 1 ● Ventilation for Healthy Living
5.3 Ventilation load during heating
●
Classification of heating load
Class
Heat lost from walls (q
WS)
(a)
Indoor heat
Heat lost from glass (q
GS)
loss
Heat loss from conduction & convection (q
GS)
Accumulated heat load in walls (q
SS)
(b)
Outdoor air
Sensible heat (q
FS)
load
Latent heat (q
FL)
During heating, the heat generated by people and electrical equipment in the room can be subtracted from the heating load. However, as the warming up time at the start of heating is short, this generated heat may be ignored in some cases.
Percentage of load
Internal heat loss
In terms of load classification, the internal heat loss is the value of the outdoor air load subtracted from the approximate heating load.
Internal heat loss = 133.7 W/m
2
– 56.0 W/m2= 77.7 W/m
2
Heating load per unit area
When the outdoor air volume per person is 25 m
3
/h, and the number of persons per 1 m2is 0.2 persons, the approximate
heating load will be approximately 133.7 W/m
2
.
●
Outdoor air load
Air conditions <Standard design air conditions in Tokyo>
Type of load Load
Outdoor air load 56.0 W/m
2
Internal heat 77.7 W/m
2
Total 133.7 W/m
2
Conditions: Middle floor of a general office building facing south.
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
Indoors 20 °C 50% 13.7 °C 38.5 kJ/kg
When the load per 1 m2of floor area with a ventilation volume of 25 m3/h·person is calculated with the above air conditions, the following is obtained:
Outdoor air (ventilation) load = 1.2 kg/m
3
× 0.2 persons/m2× 25 m3/h·person × 33.5 kJ/kg = 201.0 kJ/h·m2(56 W/m2)
The Lossnay recuperates approximately 70% of the outdoor air load and saves on approximately 30% of the total load.
Outdoor
air load 41.9%
56.0 W/m
2
Indoor heat loss 58.1%
77.7 W/m
2
133.7 W/m
2
Page 20
Page 21

CHAPTER 2
Lossnay Construction and Principle

Page 22
16
CHAPTER 2 ● Lossnay Construction and Principle

1. Construction and Features of Lossnay

● Lossnay construction
The Lossnay is constructed so that the exhaust air passage from the indoor side to the outdoor side (RA → EA) and the fresh air passage from the outdoor side to the indoor side (OA → SA) cross. The Lossnay heat recovery unit (Lossnay Core) is installed at this cross point, 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 of Lossnay
(1) Cooling and heating maintenance fees are saved while ventilating.
(2) The capacity and performance of the air conditioner can be reduced.
(3) Dehumidifying during summer, and humidifying during winter is possible.
(4) Comfortable ventilation is possible, (the outdoor air being adjusted to the room temperature.)
(5) Effective sound-proofing.

2. Construction and Principle of Core

● Simple construction
The Lossnay Core is a cross-flow total heat recovery unit constructed of plates and fins made of treated paper. The fresh air and exhaust air passages are 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 fresh air being introduced into the system when they pass through the Lossnay. Try this simple experiment. Roll a piece of paper into a tube and blow through it. Your hand holding the paper will immediately feel warm. If cold air is blown through the tube, your hand will immediately feel cool. Lossnay is a total heat exchanger that utilizes these special properties of paper.
●
Treated paper
The paper partition plates are treated with special chemicals so that the Lossnay Core is an appropriate heat recovery unit for the ventilator. This paper differs from ordinary paper, and has the following unique properties.
(1) The paper is incombustible and is strong.
(2) The paper has selective hydroscopicity and moisture permeability that permits the passage of water vapor only (including
some water-soluble gases).
(3) The paper has gas barrier properties that does not pass gases such as CO
2.
Hyper Core
The Hyper Core that utilizes the world’s thinnest* 25 µm ultra-thin film imperforate paper has been developed to further reduce gas transfer and to improve humidity exchange efficiency. The Hyper Core is mounted to the LGX-RX
4.
(* As of January 22, 2004, in the case of a high moisture permeable material used for total heat exchange elements)
SA Supply air diffuser (Fresh cold or warm air)
Partition plate (Treated paper)
Spacer plate (Treated paper)
RA Return air (Stale cold or warm air)
Indoors Outdoors
EA Exhaust air (Stale air)
OA Outdoor air (Fresh air)
Page 23
17
CHAPTER 2 ● Lossnay Construction and Principle
A comparison of the ordinary paper and the Lossnay Core plates is as shown in the table.
Ordinary paper
Water vapor is transferred, but gas elements that are easily dissolved in water such as CO
2
, NO2 are also transferred.
The contaminated air passes through the plates during ventilation and returns to the room.
Treated paper
Water vapor is transferred, but gas elements such as CO
2,
NO
2 are not transferred.
The contaminated air does not almost return to the room when ventilated.
Hyper core
The water vapor transfer rate has increased with further reduction of gas transfer.
The rate at which the contaminated air returns to the room has been reduced to less than 1%*, and the total heat exchange performance has also been improved. (* Based on data measured by Mitsubishi using a single core unit)
Low humid air
Water molecule
25 µm
Gas (CO2) molecule
Non-porous ultra-thin film material
Highly humid air
Highly humid air
Water vapor
Water vapor
CO
2 NO2
CO2 NO2
CO2 NO2Water vapor
Water vapor
Treatment (Selective permeable film) (Incombustible specifications)
Low humid air
Highly humid air
Cellulose fibers
Low humid air
● Total heat recovery mechanism
Sensible heat and latent heat
The heat that enters and leaves in accordance with changing temperature (rise or drop) is called sensible heat. The heat that enters and leaves due to the changes in 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 on the right, the heat recovery efficiency is affected by the resistance of the boundary layer, and for the Lossnay there is little difference when compared to materials such as copper or aluminium which 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 is moved through the partition plate from the high humidity to low humidity side by means of the differential pressure in the vapor.
High humidity side
Low humidity side
Partition plate
120µm
Page 24
18
CHAPTER 2 ● Lossnay Construction and Principle

3. Calculation of the Total Heat Recovery Efficiency

The Lossnay Core’s heat 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 heat recovery effect can be calculated if two of the above efficiencies is known. (The temperature and enthalpy efficiencies are indicated in the applicable catalogue.)
●
Each recovery efficiency can be calculated with the formulas given below.
●
When the supply air volume and exhaust air volume are equal, the heat recovery efficiencies on the supply and exhaust sides are the same.
●
When the supply air volume and exhaust air volume are not equal, the total heat recovery efficiency is low if the exhaust volume is lower, and high if the exhaust volume is higher. Refer to the Heat Recovery Efficiency Correction Curve in the applicable catalogue for more details.
SA Supply air (Fresh cold or warm air)
RA Return air (Stale cold or warm air)
Indoors Outdoors
EA Exhaust air (Stale air)
OA Outdoor air (Fresh air)
Item Formula
Temperature recovery efficiency (%)
ηt =
t (
OA
) - t (SA)
× 100
t (
OA) - t (RA)
Enthalpy recovery efficiency (%)
ηi =
i (
OA) - i (SA)
× 100
i (
OA
) - i (RA)
η: Efficiency (%)
t: Dry bulb temperature (°C)
i: Enthalpy (kJ/kg)
Calculation of air conditions after passing through Lossnay
If the Lossnay heat 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.
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
Page 25
19
CHAPTER 2 ● Lossnay Construction and Principle

4. What is a Psychrometric Chart?

The chart which shows the properties of humid air is called a psychrometric chart. The psychrometric chart can be used to find the (1) Dry bulb temperature, (2) Wet bulb temperature, (3) Absolute humidity, (4) Relative humidity, (5) Dew point and (6) Enthalpy (total heat) of a certain air condition. If two of these values are known beforehand, the other values can be found with this chart. The way that the air will change when it is heated, cooled, humidified or dehumidified can also be seen easily on the chart.
(1) Dry bulb temperature t (°C)
Generally referred to as standard temperature this is measured with a dry bulb thermometer (conventional thermometer). The obtained value is the dry bulb temperature.
(2) Wet bulb temperature t’ (°C)
When a dry bulb thermometer’s heat sensing section is wrapped in a piece of wet gauze and an ample air flow (3 m/s or more) is applied, the heat applied to the wet bulb by the air and the heat of the water vapor that evaporates from the wet bulb will balance at an equal state. The temperature indicated at this time is called the wet bulb temperature.
(3) Absolute humidity x (kg/kg’)
The weight (kg) of the water vapor that corresponds to the weight (kg’) of the dry air in the humid air is called the absolute humidity.
(4) Relative humidity ϕ (%)
The ratio of the water vapor pressure Pw in the humid air and the water vapor pressure Pws in the saturated air at the same temperature is called the relative humidity. This is obtained with the following formula:
ϕR = P
W/PWS × 100
(5) Dew point t” (°C)
The water content in the air will start to condense when air is cooled. The dry bulb temperature at this time is called the dew point.
(6) Enthalpy i (kJ/kg)
Physical matter has a set heat when it is at a certain temperature and state. This retained heat is called the enthalpy, with dry air at 0 °C being set at 0.
Temperature (°C)
Absolute humidity 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
Page 26
20
CHAPTER 2 ● Lossnay Construction and Principle

5. Calculation of Lossnay Heat Recovery

The following figure shows the conditions of various air states when fresh air is introduced through the Lossnay Core. If a conventional sensible heat recovery unit is used alone and is assumed to have the same heat recovery efficiency as Lossnay, the condition of the air supplied to the room is expressed by point A in the figure. This point shows that the air is very humid in summer and very dry in winter. The air supplied to the room with Lossnay 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 following formula.
Total heat recovered: qT = γ · Q · (iOA - iSA) [W]
= γ · Q · (i
OA - iRA) × ηi
Where γ = Specific weight of 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 = Heat recovery efficiency (%)
●
Suffix meanings
OA : Outdoor air RA : Return air SA : Supply air
Enthalpy (kJ/kg)
Outdoor air load
Lossnay Core heat recovery
Enthalpy (kJ/kg)
Outdoor air load
Lossnay Core heat recovery
Outdoor air
condition in
winter
Supply air condition of
the Lossnay
Supply air condition of
the Lossnay
Room air
condition
in summer
Outdoor air condition
in summer
Absolute
humidity (kg/kg’)
Room air condition in winter
Dry bulb temperature (°C)
Page 27

CHAPTER 3
General Technical Considerations

Page 28

1. Lossnay Heat Recovery Effect

1.1 Comparison of outdoor air load of various ventilators
Examples of formulas to compare the heat recovered and outdoor air load when ventilating with the Lossnay (total heat recovery unit), sensible heat recovery ventilation (sensible HRV) and conventional ventilators are shown below.
(1) Cooling during summer
Conditions
●
Model LGH-100R type
●
Heat recovery efficiency table (%)
(at 50Hz, high speed) (For summer)
●
Ventilation rate: 1000 m3/h (specific gravity of air
ρ
= 1.2 kg/m3)
22
CHAPTER 3 ● General Technical Considerations
Lossnay Sensible HRV
Conventional
ventilator
Temperature
79 79 –
(sensible heat)
Enthalpy
67 19* –
(total heat)
hOA
hSA
hRA
84.6
63.4
52.9
tOA
33
tSA
27.5
tRA
26
R
S
AO
X
OA
0.0201
XSA
0.0140
XRA
0.0105
●
Lossnay (Supply air diffuser temperature)
tSA = 33°C – (33°C – 26°C) × 0.79 = 27.5°C
(Supply air diffuser enthalpy)
hSA = 84.6 – (84.6 – 52.9) × 0.67 = 63.4 kJ/kg
Heat recovered
(84.6 – 63.4) × 1.2 × 1,000 = 25,440 kJ/h = 7.07 kW
Outdoor air load
(63.4 – 52.9) × 1.2 × 1,000 = 12,600 kJ/h = 3.5 kW
●
Sensible HRV (Supply air diffuser temperature)
tSA = 78.9°C – (33°C – 26°C) × 0.79 = 27.5°C
(Supply air diffuser enthalpy)
hSA
= kJ/kg (from psychrometric chart)
Heat recovered
(85.0 – 78.9) × 1.2 × 1,000 = 7,320 kJ/kg = 2.03 kW
Outdoor air load
(78.9 – 53.2) × 1.2 × 1,000 = 30,840 kJ/h = 8.56 kW
[Calculated enthalpy recovery efficiency 2.03 ÷ (2.03 + 8.56) × 100 = 19]
●
Conventional ventilator If a conventional ventilator is used, the heat recovered will be 0 as the supply air diffuser is equal to the outdoor air. The outdoor air load is: (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 heat recovery
Outdoor air load
Enthalpy
(kJ/kg)
Supply air
Room air
Air
conditioner
Lossnay Sensible HRV
Conventional
ventilator
Dry bulb temperature
Absolute humidity
Relative humidity
Enthalpy
26°C
27.5 27.5 33
14.0 20.1 20.1
61 86 63
63.4 78.9 84.6
7.1 20.0 0
3.5 8.6 10.6
33 81 100
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)
Outdoor air load (kW)
Outdoor air load ratio (%)
Total heat recovered (kW)
* Calculated volume under below conditions.
Page 29
(2) Heating during winter
Conditions:
●
Model LGH-100R type
●
Heat recovery efficiency table (%)
(at 50Hz, high speed) (For winter)
●
Ventilation rate: 1000 m3/h (Specific gravity of air
ρ
= 1.2 kg/m3)
23
CHAPTER 3 ● General Technical Considerations
Lossnay Sensible HRV
Conventional
ventilator
Temperature
79 79 –
(sensible heat)
Enthalpy
71 47* –
(total heat)
Supply air
Room air
Air
conditioner
Lossnay Sensible HRV
Conventional
ventilator
Dry bulb temperature
Absolute humidity
Relative humidity
Enthalpy
20°C
15.8 15.8 0
5.1 1.9 1.9
46 17 50
28.7 20.7 4.7
8 5.3 0
3.3 5.9 5.6
29 47 100
7.2 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)
Outdoor air load (kW)
Outdoor air load ratio (%)
Total heat recovered (kW)
●
Lossnay (Supply air diffuser temperature) tSA=
(20°C – 0°C) × 0.79 + 0°C = 15.8°C
(Supply air diffuser
enthalpy)
hSA=
(38.5 – 4.7) × 0.71 + 4.7
=
28.7 kJ/kg
Heat recovered (28.7 – 4.7) × 1.2 × 1,000
= 28,800 kJ/h = 8.0 kW
Outdoor air load (38.5 – 28.7) × 1.2 × 1,000
=
11,760 kJ/h = 3.3 kW
●
Sensible HRV (Supply air diffuser temperature) tSA=
(20°C – 0°C) × 0.79 + 0°C = 15.8°C
(Supply air diffuser
enthalpy)
hSA=
20.7 kJ/kg (from psychrometric chart)
Heat recovered (20.7 – 4.7) × 1.2 × 1,000
= 19,200 kJ/h = 5.3 kW
Outdoor air load (38.5 – 20.7) × 1.2 × 1,000
= 21,360 kJ/h = 5.9 kW
[Calculated enthalpy recovery efficiency 5.3 ÷ (5.3 + 5.9) × 100 = 47]
●
Conventional ventilator If a conventional ventilator is used, the supply air diffuser is the same as the outdoor air and the exhaust is the same as the room air. Thus the heat recovered is 0 kcal and the outdoor air 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
tSA
15.8
tRA
20
R
S
O
A
X
RA 0.0072
XSA 0.0051
XOA 0.0019
hSA
38.5
4.7
28.7
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
heat recovery
Outdoor air load
Enthalpy
(kJ/kg)
* Calculated volume under below conditions.
Page 30
24
CHAPTER 3 ● General Technical Considerations

2. Example Heat Recovery Calculation

(1) Setting of conditions
(Note: Tokyo Power, industrial power 6 kV supply)
●
Return air volume (RA) = 8,000 m3/Hr
●
Outdoor air volume (OA) = 8,000 m3/Hr
●
Air volume ratio (RA/OA) = 1.0
●
Air conditions
(2) Selection of Lossnay model (select from treatment air volume catalogue)
●
Model name: LGH-100RX4 × 8 unit
●
Processing air volume per unit RA = 8,000 m3/Hr, OA = 8,000 m3/Hr, Air volume ratio (RA/OA) = 1.0
●
Heat recovery efficiency : Heat recovery efficiency = 79%, Enthalpy recovery efficiency (cooling) = 67%,
Enthalpy recovery efficiency (heating) = 71%
●
S
tatic pressure loss (unit-type) RA = 100 Pa, OA = 100 Pa (Note: Each motors are High notch)
●
Power consumption (pack-type) = 440W × 8 unit
= 3.52 kW
(3) State of indoor supply air
(4) Outdoor air load and heat recovered
(5) Recovered money (power rates)
Units When Heating When Cooling
Operation time (h/yr)
10h/day × 26 days/mo. × 5 mo./yr. = 1,300 h/yr 10h/day × 26 days/mo. × 4 mo./yr. = 1,040 h/yr
Electricity fee
(yen/kWh)
16.22 17.84
Capacity per
(kW/kW) 3.1 2.6
1 kW of electricity
Energy unit cost
(yen/kWh)
16.22/3.1 = 5.23 17.84/2.6 = 6.86
Season Winter heating Summer cooling
Item
Dry bulb temp
.Wet bulb temp.
Relative humidity
Absolute humidity
Enthalpy h Mark
Dry bulb temp.
Wet bulb temp.
Relative humidity
Absolute humidity
Enthalpy h Mark
DB [°C] WB [°C] RH [%]
× [kg/kg (DA)]
[kJ/kg (DA)]
in page 25 DB [°C] WB [°C] RH [%]
× [kg/kg (DA)]
[kJ/kg (DA)]
in page 25
Outdoors
0 –2.7 50 0.0018 4.7
1
33 27.1 63 0.0202
85.0 (20.3)
3
Indoors 20 13.8 50 0.0072 38.5
2
26 18.7 50 0.0105
53.0 (12.7)
4
Heating Cooling
= { 20 (Indoor temperature) – 0 (outdoor air temperature)} × = 33
(Outdoor air temperature) – { 33 (outdoor air temperature) –
Temperature [°C] 0.79 (heat recovery efficiency) + 0 (outdoor air temperature) 26 (indoor temperature)} × 0.79 (heat recovery efficiency)
= 15.8 = 27.5
Enthalpy
= {38.5 (Indoor enthalpy) – 4.7 (outdoor air enthalpy)} × = 85 (Outdoor air enthalpy) – { 85 (outdoor air enthalpy) –
[kJ/kg (DA)]
0.71 (enthalpy recovery efficiency) + 4.7(outdoor air enthalpy)
53
(indoor enthalpy)} × 0.67 (enthalpy recovery efficiency)
= 28.7 = 63.6
Numerical value obtained •Dry-bulb temperature = 15.8 °C •Wet-bulb temperature = 9.9 °C•Dry-bulb temperature = 27.5 °C •Wet-bulb temperature = 21.8 °C
from above equation and •Relative humidity = 46% •Absolute humidity = 0.005 kg/kg (DA)•Relative humidity = 61% •Absolute humidity = 0.014 kg/kg (DA)
psychometric chart•Enthalpy = 28.7 kJ/kg (DA) (page 25,
5
)
•
Enthalpy = 63.3 kJ/kg (DA) (page 25, 6)
Heating Cooling
Fresh air load without
= 1.2 (Air specific gravity) × 8,000 (outdoor air volume) × = 1.2 (Air specific gravity) × 8,000 (outdoor air volume) ×
Lossnay (q
1)
{ 38.5 (indoor enthalpy) – 4.7 (outdoor air enthalpy) } { 85.0 (outdoor air enthalpy) – 53.2 (indoor enthalpy) }
= 324,480 kJ/h = 90.1 kW = 307,200 kJ/h = 85.3 kW
= 90.1 (Outdoor air load) (q
1) × = 85.3 (Outdoor air load) (q1) ×
Outdoor air load with
{ 1 – 0.71 (enthalpy recovery efficiency)} { 1 – 0.67 (enthalpy recovery efficiency) }
Lossnay (q
2)
= 26.1kW = 28.2 kW
or or
=
Air specific gravity × outdoor air volume × (indoor enthalpy – indoor blow enthalpy)
=
Air specific gravity × outdoor air volume × (indoor enthalpy – indoor blow enthalpy)
= q1 – q2 = q1 – q2 = 90.1 - 26.1 = 85.3 - 28.2
Heat recovered (q
3)
= 64.0 kW = 57.1 kW
or or
= Outdoor air load (q1) × enthalpy recovery efficiency = Outdoor air load (q1) × enthalpy recovery efficiency
•
Outdoor air load = 90.1 kW = 100%
•
Outdoor air load =85.3 kW = 100%
Outdoor air load (%)•Outdoor air load with Lossnay = 26.1 kW = 29%
•
Outdoor air load with Lossnay = 28.2 kW = 33%
•
Heat recovered = 64.0 kW = 71%
•
Heat recovered = 57.1 kW = 67%
Heating Cooling
=
Heat recovered: kW ×Unit price yen/W ×operation time Hr/year = Heat recovered: kW × Unit price yen/W × operation time Hr/year
Yearly saved money = 64.0 kW × 5.23 yen/kWh × (1,300hr/year) = 57.1 kW × 6.86 yen × (1,040hr/year)
= 435,100 yen = 407,374 yen
Remarks If recovered heat is converted to electricity : heating = 64.0 kW/3.1 = 20.6 kW/h cooling = 57.1 kW/2.6 = 22.0 kW/h
Page 31
25
CHAPTER 3 ● General Technical Considerations
●
Psychrometric chart for calculating Lossnay economical effect
The following can be determined from the above calculation results:
●
Saving of 64.0 kW of the heating load, and 57.1 kW of the cooling load is possible. The heat source equipment and related ventilator capacity that is equivalent to this saved amount can be reduced, thus the operation and maintenance costs can also be saved.
●
Approximately 430,000 yen can be saved in operation and maintenance costs during heating and 400,000 yen during cooling, for a total savings of approximately 830,000 yen.
28.7
38.5
53.2
63.3
85.0
4.7
0 15.8 20 26 33
0.0018
0.005
0.0072
0.0105
0.0146
0.0203
27.5
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
T.FUJITA
1987
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
ψ50
ψ50
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/kg]
dh
dx
Sensibleheatratio
SFH
Saturation [%]
0.94
0.92
0.93
0.96
0.95
Wetbulbtemperaturet'[°C]
Drybulbtemperaturet[°C]
Relativehum
idity[%]
Chilled
Water
Specificcapacityv [m
3
/kg(DA)]
1
5
2
4
6
3
Page 32
26
CHAPTER 3 ● General Technical Considerations

3. Calculation of Lossnay Economical Effects

The following is a sample questionnaire from which it is possible to assess the economical benefits of using the Lossnay in particular applications.
(1) Setting of 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) Selection of Lossnay model (select from treatment air volume catalog)
●
Model name:
●
Processing air volume per unit RA = m3/Hr, OA = m3, Air volume ratio (RA/OA) =
●
Heat recovery efficiency :
Heat 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) State of indoor blow air
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]
heat recovery efficiency + outdoor air temperature – indoor temperature) × temperature heat 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
==
Numerical value
●
Dry-bulb temperature = °C
●
Dry-bulb temperature = °C
obtained from above
●
Wet-bulb temperature = °C
●
Wet-bulb temperature = °C
equation and
●
Relative humidity = %
●
Relative humidity = %
psychometric chart
●
Absolute humidity = kg/kg’●Absolute humidity = kg/kg’
●
Enthalpy = kg/kg●Enthalpy = kg/kg
Page 33
27
CHAPTER 3 ● General Technical Considerations
(4) Outdoor air load and heat recovery
Heating Cooling
Fresh air load without
= Air specific gravity × outdoor air volume = Air specific gravity × outdoor air volume
Lossnay (q1)
× (indoor enthalpy
–
outdoor air enthalpy) × (outdoor air enthalpy – indoor enthalpy)
==
= Outdoor air load (q
1) = Outdoor air load (q1)
× ( 1 – enthalpy recovery efficiency) × ( 1 – enthalpy recovery efficiency) Outdoor air load with = = Lossnay (q
2)or or
= Air specific gravity × outdoor air volume = Air specific gravity × fresh air volume
× (indoor enthalpy
–
indoor blow enthalpy) × (indoor blow enthalpy – indoor enthalpy)
=q
1
–
q
2 =q1
–
q2
=
–
=
–
Heat recovery (q3)
==
or or
= Outdoor air load (q
1)=Outdoor air load (q1)
× enthalpy recovery efficiency × enthalpy recovery efficiency
● Outdoor air load = W = % ● Outdoor air load = W = %
Outdoor air load (%)
● Outdoor air load with Lossnay ● Outdoor air load with Lossnay
= W = % = W = %
● Heat recovered = W = % ● Heat recovered = W = %
(5) Recovered money (power rates)
Heating Cooling
=
Heat recovered: kW × Unit price ¥/kWh ×
=
Heat recovered: kW × Unit price ¥/kWh ×
Yearly saved money
operation
time Hr/year = kW ×
¥
/
kWh
×
operation
time Hr/year = kW ×¥/
kWh
×
(
yen)
= Hr/year = Hr/year ==
Page 34
28
CHAPTER 3 ● General Technical Considerations

4. 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
Page 35
29
CHAPTER 3 ● General Technical Considerations
5.
The Result of No Virus (phage) Cross Contamination for the Lossnay
Core and Determining Resistance of the Lossnay Core to Molds
Test report
This document reports the result that there is no virus (phage) cross contamination for the Lossnay Core.
(1) Object
The present test was conducted to verify that there is no airborne virus (phage) cross contamination from the outlet air to the inlet air of the Lossnay Core in the heat exchange process.
(2) Client
Name: Mitsubishi Electric Corporation Nakatsugawa Works Address: 1-3 Komaba-cho, Nakatsugawa-shi, Gifu, Japan
(3) Institution and Analyst
Name: Kitasato Research Center of Environmental Sciences Address: 1-15-1 Kitasato, Sagamihara-shi, Kanagawa, Japan Analyst: Microbiology Department
shunji Okuda, Noriko Shimasaki
(4) Test Period
December 22, 2004 (Test materials was operated by engineers of your company)
(5) Test Materials
New Lossnay core “Hyper Element*”
(6) Organism
1) Test virus
E.coli phage ϕX174 ATCC 13706-B
2) Host bacteria
Escherichia coli ATCC 13706
3) Host bacteria culture
Escherichia coli (explained in 2)) was inoculated into 0.5% Nacl-added Nutrient Broth (Difco), and was cultivated overnight at 35:. The resultant medium containing approximately 10
9
CFU/ml of host becteria was used as host becterium solution.
4) Test virus solution
E.coli phage ϕX174 was mixed with host bacterium solution (explained in 3)) and cultivated. The resultant medium was filtrated by membrane filter owing to removal of Escherichia coli, and was diluted with sterile ion-exchanged water to obtain test virus solution of approximately 10
7
PFU/ml.
(7) Method
1) Outline
The test apparatus is schematically shown in Fig. 1. The air flow rate was 250m
3
/hr in the outlet and inlet ducts intersecting each other at the Lossnay Core. Air-sampling tubes were attached, with their openings against the air flow, at the each center of 4 sites, outlet duct upstream (location A) and downstream (location B) and inlet duct upstream (location C) and downstream (location D) of the Lossnay Core. The test was performed as follows: Test virus solution was sprayed from the upstream side of the outlet duct, and a specified quantity of air was then simultaneously sampled with midget impingers at 4 sites, locations A, B, C, and D around the Lossnay Core to count the number of airborne viruses contained in the air.
Page 36
30
CHAPTER 3 ● General Technical Considerations
2) Spray of test virus solution
The test virus was sprayed in the outlet duct at a pressure of 1kgf/cm
2
while supplying compressed air from the
compressor into the nebulizer containing the test virus solution.
3) Sampling of airborne viruses
Airborne viruses were collected using the midget impinger as described below. Air in the duct was aspirated at a rate of 5 liters per minute for 4 minutes. Hence, a total of 20 liters of air was collected in 25 ml of sterile ion­exchanged water in the midget impinger.
4) Method for counting the number of viruses
Ion-exchanged water in the midget impingers, which possibly contained airborne viruses (E.coli phages), was used as the sample stock solution, and its 10-fold serial dilutions were then made. 0.2 ml of the stock solution and each
dilution were mixed with 0.2 ml of host becterium solution of about 10
9
CFU/ml, and then mixed with 4.0 ml of soft
agar for top layer. The mixture was then layered on the surface of 0.5% NaCl-added Nutrient Agar. The resultant medium was incubated for 18 hr at 35:. The number of plaques formed was counted to determine the number of
airborne viruses per 20L of sampled air.
(8) Test result
The concentration of test virus solution was 1.2X107 PFU/ml. The result of test is shown in table-1.
(9) Consideration
The test virus was E. coli phage ϕX174 with a small viral particle diameter (about 20 nm). Test viruses were detected at locations A and B on the outlet side, from which the test virus solution was sprayed. In contrast, no test viruses were detected in 20L of sampled air at location C (in the air filtered by the ULPA filter) or location D (in the air crossed in the Lossnay Core) on the inlet side. Therefore, it can be concluded that airborne viruses in the outlet side will not cross the dividers (specially processed paper) of the Lossnay Core to the opposite inlet side even when heat is exchanged there.
Teble-1 Airborne virus counts on each location
Test virus : E.coli phage ϕX174 ATCC 13706-B
(Unit of measurement: PFU/20L-air)
Test No. Location A Location B Location C Location D
1 3.1 X 10
2
2.8 X 10
2
< 1 < 1
2 4.4 X 10
2
1.2 X 10
2
< 1 < 1
3 1.9 X 10
2
6.2 X 10 < 1 < 1
Average 3.1 X 10
2
1.5 X 10
2
< 1 < 1
A
Outlet duct Lossnay Core
Inlet duct
Neblizer
Compressor
Safety cabinet Safety cabinet
ULPA filter ULPA filter
D
MI
MI
MI
MI
C
B
* MI : Midget impinger
* Hyper Element is LGH-RX4 series core.
Note: Above test concluded that airborn viruses which is about 0.02µm will not cross the paper of Hyper Element.
In the other test used Bacillus Subtillis and Serratia Marcescers which are about 0.5 - 0.3µm, their Bacteria do not cross the core paper for LU-500 and LGH-40ES.
Page 37
31
CHAPTER 3 ● General Technical Considerations
Material, Mixture ratio, Organization, Fan number, Density, Weight (g/m
2
)

6. Flame-proofing Properties of Lossnay Core

The Lossnay Core satisfied all requirements of Paragraph 4-3 of the Fire Prevention Law Enforcement Rules. Details of the tests carried out are as seen below.
Notation format 2 - (3)
Notification of flame-proofing property test
(For flame-proof materials and related items)
Flame-proofing committee test No., B-80028 April 17, 1980
Messrs.: Mitsubishi Electrical Corporation
Japan Flame-proofing committee
The results of the test, requested on April 8, 1980, are as follows.
Whereas
Part name
Product name (Brand)
Air filter To tal heat recovery unit
Lossnay (ventilation fan) B
Specially treated paper:
(Partition (white) : Thickness 0.2 mm) (Filler block (blue) : Thickness 0.2 mm)
Adhesive agent:
Vinyl acetate (Specific gravity ratio 2.6%) 600 g/m
2
Residual Residual
Carbonized
Test No. Test item flame dust area
(sec.) (sec.) (cm
2
)
1
0. 4.1 35.4
(Vertical)
2-min. 2
0. 7.7 38.2
heating (Vertical)
3
0. 1.4 35.9
(Horizontal)
6-sec.
1
0. 0. 26.3
heating after
(Vertical)
igniting
2
0. 0. 20.3
(Horizontal)
Test item Carbonization No. of flame
length
contact times
Test No. (cm) (times)
1
2
3
4
5
Evaluation Passing
Remarks
Test method
Application of Paragraph 4-3 Standards of Fire Prevention Laws Enforcement Rules (Ministry of Home Affairs Ordinance No. 6, 1961) (Thick cloth test)
Passing standards
Residual flame : 5 sec. or less Residual dust : 20 sec. or less Carburized area : 40 cm
2
or less
Washing test
Page 38
32
CHAPTER 3 ● General Technical Considerations
Applicant
Company name Mitsubishi Electric Corp., Nakatsugawa Works
Address 1-3 Komanba-cho, Nakatsugawa, Gifu
Specimen type
Single-face laminated Product Lossnay Core corrugated board name (Total heat recovery unit)
Single-face laminated corrugated board
... Thickness: 4 mm (Single-face corrugated board with 2 mm cell size laminated alternately at right angle) Partition (Liner paper) Flame-proof treated paper
...
Thickness: 0.085 mm, Weight: 70 g/m
2
Material structure and Adhesive agent ... Vinyl acetate resin
Specimen cross-sectional ... Weight: 30 g/m
2
(Solid)
and test body
diagram, etc.
Filler (Flute paper)
... Colored wood free paper
...
Thickness: 0.093 mm, Weight: 79 g/m
2
Adhesive agent
... Vinyl acetate resin
... Weight: 30 g/m
2
(Solid) Partition (Liner paper) Flame-proof treated paper
...
Thickness: 0.085 mm, Weight: 70 g/m
2
Test body size and
300 (Long side) × 200 (Short side) × 4 (Thickness)
thickness (mm)
Test body direction The longer side is the vertical side.
Testing standards
Pre-treatment of Heating
Heating surface class and direction
Testing
test body time
method
JIS A 1322
Method A
The direction of which the corrugated
(45° Meckelian burner
(drying method)
3 min. board fold was vertical was set as the
method) front of the heating surface.
Test date October 5, 1993
Test position
Residual Residual
Carbonized Discoloration
frame dust
length (Vertical ×length (Vertical ×Remarks
Test results
Class Direction No. (sec.) (sec.)
Horizontal) (cm) Horizontal) (cm)
10 08.2 × 4.7 18.7 × 7.3
Front Vertical 2 0 0 8.4 × 4.9 24.3 × 7.8 *1
30 07.4 × 5.0 22.0 × 8.4
Evaluation
The specimen conforms to Class 2 flame-proofing (heating time: 3 min.) according to the “Fire retardancy test methods of thin materials for construction” as set forth by JIS A 1322.
Material Testing Laboratory
Persons in charge of testing Laboratory chief: Hiroshi Tamura, Technicians: Shigeru
Fujikawa, Nobuaki Oohiro, Tetsuya Ogawa
The Lossnay Core was also tested at the Japan Construction General Laboratories according to the fire retardancy test methods of thin materials for construction as set forth by JIS A 1322. The material was evaluated as Class 2 flame retardant. Details of the tests carried out are shown below.
Flame-proofing property test report
Messrs. Mitsubishi Electric Corp.,
Nakatsugawa Works
Acceptance No. VF-93-11-(2)
Data of acceptance September 7, 1993
Data of report October 12, 1993
Japan Construction General Laboratories
5-8-1 Fujishirodai, Suita City 565
Tel: 06-872-0391
Hiorshi Wakabayashi Dr. of Engineering, Director
Note: Immediately after starting heating, the flame was ignited simultaneously with the generation of smoke. Penetration was
observed approx. 2 min. 30 sec., after heating was started. There were no further changes. In above test the Lossnay core material for LU and LGH-40ES type is used. Hyper Element paper for LGH-RX4 series was tested at the Underwriters Laboratories Inc. according to the standard of UL94, Test for Flammability of Plastic Materials for Parts in Devices and Appliances, 1998. The material was evaluated as per 5VA classified of flammability.
4mm
2mm
Page 39
33
CHAPTER 3 ● General Technical Considerations

7. Lossnay Core’s Soundproofing Properties Test

As the Lossnay Core is made of paper and the permeable holes are extremely small, the Core has outstanding soundproofing properties and is appropriate for ventilation in soundproof rooms. For example, the exposed ceiling-type LGH-100RX3-E has soundproofing characteristics of 35.0dB with a center frequency of 500Hz. This means that a sound source of 84.4dB can be shielded to 49.4dB.
* Page 4 is in the certificate of this test.
Soundproofing effect test results
Test number
Name
Client
Address
Trade name
Main composition
Manufacture date
Size (unit : mm)
Test specimenTest results
IVA-01-06
Mitsubishi Electric Corporation 1-3, Komaba-cho, Nakatsugawa-shi,
Gifu 508-8666, Japan
LGH-100RX
3-E
Air-to-Air Energy Recovery Ventilator
May. 18th, 2001
W1231 ✕ H398 ✕ D1521
(ANNEXED DRAWINGS No.1,2 show details.)
Pipe joint in the sound receiving room side (Portion A in ANNEXED DRAWING No.1) had
Note
been filled with oil clay and then winded with onefold aluminum tape, sound insulation sheet and glass wool around duct successively.
Date of test Sound transmitting size Air temperature, Relative humidity
Center
frequency
1000
1250
1600
2000
2500
3150
4000
5000
Average sound pressure level (dB)
(Hz)
100
125
160
200
250
315
400
500
630
800
Source
room Ls
83.3
83.8
85.5
86.0
86.1
85.0
86.2
84.4
84.7
85.5
87.0
89.2
89.3
90.7
92.8
83.4
95.0
95.0
Receiving
room Lr
59.3
62.8
61.0
58.7
58.3
57.0
54.3
49.4
50.7
48.7
47.7
47.7
47.4
47.0
48.2
48.2
48.8
47.6
May. 18th, 2001
φ254 mm ✕ 2
22.0°C, 62%RH (Receiving room)
Level
difference D
24.0
21.0
24.5
27.3
27.8
28.0
31.9
35.0
34.0
36.8
39.3
41.5
41.9
43.7
44.6
45.2
46.2
47.4
Equivalent absorption
area in receiving
room A (m2)
2.65
3.21
3.69
3.48
3.54
3.96
4.40
4.62
4.80
5.06
5.58
6.26
7.03
7.57
8.62
10.19
12.42
15.51
Sound
transmission
loss
TL (dB)
10
6
9
12
12
12
16
18
17
20
22
24
23
25
25
25
25
26
Note
1. The left graph shows level difference with (revised) sound transmission loss.
2. Page 4* shows method of calculating (revised) sound transmission loss.
3. Test specimen area (Sound transmitting area) is S = 0.10134m
2
(φ254mm ✕ 2)
for calculating (revised) sound transmission loss.
4. An arithmetic mean of revised sound transmission loss (1/3 octave, 125Hz
- 4000Hz)....18.4dB
Test method was determined according to JIS A 1416 : 1994 "Method for laboratory measurement of sound transmission loss" and Architectural Institute of Japan Standard "Measurement method on sound transmission loss of small
Standard
building elements".
(Reverberation room No.2)
3
178.5m
180.0m
Test specimen
MIC.
Computer system
Printer
Chain block (2t)
Sound receiving side
Test specimen
Test method
5560
Section
Test
laboratory
(Reverberation room No.3)
300
300
Air layer (t50)
Sound source side
Neoplane rubber
Filled sand
Cavity concrete block (t190) Filled inside with sand Mortared both side (t15)
F. L.
Volume
Fig. 1 Testing setup (unit : mm)
Heat & Acoustics Laboratory, Building Physics Dept. General Building Research Corporation of Japa 5-8-1 Fujishirodai, Suita-shi, Osaka 565-0873, Japan
Revised sound transmission
loss
TLc (dB)
11
6
10
70
Air-to-Air Energy
Recovery Ventilator
60
LGH-100RX
3-E
13
13
12
16
19
17
50
Level difference between the source room and the receiving room
40
20
22
24
23
25
30
Sound transmission loss (dB)
20
Revised sound transmission loss
25
25
25
10
Sound transmission loss
26
0
125 250 500 1000 2000 4000
Center frequency (Hz)
The persons in charge of the test
Iwao Kurahashi (Head) Takao Waki (Section chief) Mitsuo Morimoto (Section chief)
Sound source sideSound receiving side
3
Test specimen
SP.
Amplifier2ch selector
EqualizerReal time analyzer
Noise generator
Page 40
34
CHAPTER 3 ● General Technical Considerations

8. Change in Lossnay Core Over Time

The following details show an example of a building that has installed the Lossnay units, from which it is possible to assess the change in the units over time.
8.1 Outline of building where Lossnay is installed
(1) Building name : Meiji Seimei, Nagoya Office/shop building
1-1 Shinsakae-machi Naka-ku, Nagoya
(2) No. of floors : 16 above ground, 2-storey penthouse, 4 basement floors
(3) Total floor space : 38,893 m
2
(4) Reference floor space : 1,388 m
2
8.2 Outline 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 1630 kW
(2) Ventilation method : Air - air total heat 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 outline diagram : 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 General diagram of penthouse Lossnay chamber
Unit (mm)
Exhaust air
OA side by-pass damper
Lossnay
RA fan
(for
exhaust)
Outdoor air
OA fan
(for intake)
RA side
by-pass damper
* Core pertition plate pitch is same as LGH-RX4-E series.
It is narrower than pitches of both LGH-40ES and LU-500.
Page 41
35
CHAPTER 3 ● General Technical Considerations
8.3 Outline of Lossnay operation
(1) Start of operation : September 1972
Start of daily operation : 7:00
Average daily operation 11 hours
End of daily operation : 18:00
(2) Inspection after usage : November 1983
(3) Bypass operation month : Three months of April, May, June
(4) Total operation time : (134 – 33) months × 25 days/month × 11 hours/day = 27,775 hours
8.4 Characteristics in change of Lossnay Core over time
Two Lossnay Cores were removed from the 18 Lossnay LS-200 installed in the Meiji Seimei Building, and the static pressure loss and exchange efficiencies were measured. The comparison with the initial value is shown on the right. The appropriate air volume
for one Lossnay Core is 500 m
3
/hr, and the measurement point
was ±200 m
3
/hr of this value.
300
0
10
20
60
30
70
80
90
500 700
Characteristics in change of Lossnay Core over time
8.5 Conclusion
(1) Changes in the characteristics of the Lossnay Core after approximately eleven years of use and an estimated 28,000
operation hours were not found.
In numerical values, the static pressure loss was 150 to 160 Pa at 500 m
3
/hr which was a 10 Pa increase, and the
exchange efficiencies had decreased slightly at above 500 m
3
/hr. However, this is considered to be insignificant and
remained in the measurement error range.
(2) Looking at the appearance, the Core surface was black with dust, but there were no gaps, deformation or mold that would
pose problems during practical use.
}
Data from delivery (1974) Data from 1983
Treated air volume (m3/h)
Heat recovery efficiency
Enthalpy recovery efficiency during heating
Static pressure Loss
Static pressure loss (mmH2O) Recovery efficiencies (%)
Page 42
36
CHAPTER 3 ● General Technical Considerations

9. Comparison of Heat Recovery Techniques

The methods by which heat recovery devices can be categorised may be considered as follows:
Basic methods of total heat exchangersa
Country of
Type Method Air flow
development
Static Conductive Cross-flow Japan
Heat recovery (Mitsubishi Lossnay) transmission type principle
Rotary type Heat accumulation/ Counterflow Sweden
humidity accumulation type
9.1 Principle construction of rotary-type
●
The rotary-type heat recovery unit is composed of 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 is rotated eight times a minute by the drive motor.
●
The principle of this rotary-type is for example when cooling, the high temperature and high humidity fresh air passes through the rotor, with the heat and humidity being absorbed by the rotor. As the rotor is rotating, it moves into the exhaust air passage, and the heat and humidity is discharged to outdoors because the exhaust is cool and has a low humidity. The rotor rotates and returns to the fresh air passage to absorb the heat and humidity again.
●
Function of purge sector There are two separation plates (purge sector) in the front and back of the rotor to separate the flow of the air. As one of the plates is slightly shifted, part of the fresh air always flows into the exhaust air passage to prevent the exhaust air and fresh air from mixing. (A balanced pressure difference is required.)
A
Vs
B
Vr
When a purge sector is mounted, the introduction of the exhaust air in the rotor to the air on the supply side can be prevented. Vr: Rotor speed, Vs: Air speed in relief section
Approx. 1.5 ø
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 sir
Return air
Rotor rotation direction
Page 43
37
CHAPTER 3 ● General Technical Considerations
9.2 Comparison of static-type and rotary-type heat recovery units
Item
Construction/ principle
Moving parts
Material quality
Mounting of prefilter
Element clogging
Air leakage Gas transmission rate
Bacteria transmission rate
Operation during off-seasons
Maintenance
Life
Model system and comparison
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 heat 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 element air
passage surface. However, this is easily removed with a vacuum cleaner.)
Approximately 2.5% air leak at standard fan position. Leaks 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 (As air intake/exhaust are separate,
transmission is low.)
Bypass circuit required (OK 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) (The static-type does not break.)
o
Available from small to large. Example
o
Characteristic design of small LU-1605 and medium models possible. Large models are easy to match to 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 is free according to combination.)
Rotary-type
<Heat accumulation/humidity accumulation­type: counterflow> The rotor core is composed of honeycomb-shaped kraft paper, etc., to which a moisture absorbent is applied (lithium chloride, etc.). This rotor is rotated, and heat accumulation/humidity accumulation ­heat discharge/humidity discharge of total heat exchange is performed by passing the exhaust and intake airs into a honeycomb passage.
× Supply air and exhaust airs flow into the same air
passage because of the rotary-type construction.
× Used (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. Thus, it cannot be removed easily and the air volume decreases.)
× Purged air volume occurs
To prevent leakage of exhaust to the air intake side, a purge air volume (6 to 14%) leak is created to the exhaust side. Thus, there are problems in the purge sector operation conditions (pressure difference, speed), and the air volume balance must be balanced.
×
Gas transmission (Ammonia : 45-57%,
hydrogen sulfide : approx. 3.2-4%)
× High (As air intake/exhaust 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, causing drainage.)
Core
cleaning: Once every one to two years Cleaning is difficult as dust is smeared into core with the 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 according to the rotor bearings and 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
●
High
o
Average × Poor
Page 44
Page 45

CHAPTER 4
Characteristics

Page 46
40
CHAPTER 4 ● Characteristics

1. How to Read the LGH Series Lossnay Characteristic Curves

1.1 Obtaining characteristics from static pressure loss
(1) Static pressure loss from straight pipe duct length (at required air volume)
(2) Static pressure loss at curved section (at required air volume)
(3) Static pressure loss of related parts (at required air volume)
Total static pressure loss
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 the 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 parts such as ducts for the air distribution. If the static pressure increases, the air volume will decrease. The air volume - static pressure curve (Q-H curve) shows this percentage. A static pressure of 19.6 Pa is applied on
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 is the curve that shows how the static pressure is applied when a 10 m duct is connected. The intersecting point A with the Lossnay Q-H curve is the operation point. This calculation should be done for both SA and EA.
Duct resistivity curve
The duct resistivity curve shows how much static pressure a duct will apply on the Lossnay, as explained above.
In general, the interrelation between the duct and static pressure is as follows:
500m3/h
19.6 Pa
L = 10m
A
20 m
15 m
10 m
5 m
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)
Q-H curve
Static pressure
Duct resistivity curve
Air volume
Air volume
Static pressure
(Duct length)
Page 47
How to read Table 3
Select the unit as per each duct. In the above example, the 520 rectangular pipe only goes as far as 17. Thus, the long side, short side and converted circular pipe values are all multiplied by 100. The point 560 where the two lines cross is hence the value where the rectangular pipe equates to the circular pipe.
41
CHAPTER 4 ● Characteristics
Reference
●
The pressure loss caused by the outdoor air is as follows:
Pressure loss caused by outdoor air (Pa)
=
r
× V
2
=
1.2 × (velocity)
2
22
r:Air weight 1.2 kg/m
3
v:Velocity (m/s)
2.2 Calculation of duct pressure loss
When selecting a model that is to be used with a duct, calculate the volumes according to Tables 3, 4, 5 and 6, and then select the unit according to the air volume and static pressure curve.
{
(2) How to obtain the duct resistivity
Table 4 Circular duct friction loss
(steel plate duct, inner roughness ε = 0.18 mm)
(1)
Calculation of a rectangular pipe
Table 3 Conversion table from
rectangular pipe to circular pipe
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
4
3
2
1
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
9
8
7
6
5
18
16
14
12
10
25
20
35
30
45
40
250
200
350
300
90
80
70
60
50
180
160
140
120
d=100cm
d=400cm
d=500cm
3
10
20
30
40
50
100
200
4
5
6
7
8
9
10
15
20
25
30
40
6
7
8
9
10
15
20
25
30
40
V=50m/s
V=50
How to read Table 4
The point where the line of the circular duct diameter (leftward slanting line) and of the required air velocity (horizontal line) intersect is the pressure loss per 1 m of duct. The value of the slanted line to the lower right of the intersecting point is the average velocity.
(Outline of Table 4)
Long side of
rectangular pipe
Circular pipe diameter
The circular pipe diameter having equal hydraulic radius
Short side of rectangular pipe
Air volume (m
3
/h)
Friction loss (Pa/m)
0.1 0.2 0.4 0.6 0.8 1.0 2.0 4.0 6.0 8.010 20 30 40 50 60 80 100
Friction loss
0.1 0.2 0.4 0.6 0.8 1.0 2.0 4.0 6.0 8.010 20 30 40 50 60 80 100
2.0
5.2
5.2
560mm
Air volume: 7000 m
3
/h
Duct diameter
Average
velocity
8 m/s
Resistance
1.17Pa/m
20
60
80
100
120
140
160
180
40
24 6 81012 14 16 18
Outdoor air pressure (Pa)
Outdoor air (m/s)
Calculation of duct pressure loss for 150,200RX4
Hypothetical curve for one of upper and lower units is 1/2 of 150,200RX4 specification curve on the horizontal line of some static pressure. Calculating each unit, use this curve as the specification curve. Specification curve for 200 and 150RX
4 type are combine of indoor and outdoor duct
pressure loss in the condition that 2 of upper and lower units are same specification.
* Duct length of specification curve is not sum of each doct of upper and lower unit.
150,200RX4 specification curve
Hypothetical curve for one of upper and lower units
Air volume
Static pressure
Page 48
42
CHAPTER 4 ● Characteristics
The figure obtained from Table 4 must then be corrected for duct type at various velocities. This can be done using Table 5 below.
Ta ble 5 Friction coefficient compensation table
An alternative, more detailed method for determining the pressure loss in duct work is as shown using the following formula:
Duct inner surface Example
Average velocity (m/sec)
5101520
Very rough surface Concrete finish 1.7 1.8 1.85 1.9
Rough Mortar finish 1.3 1.35 1.35 1.37
Very smooth Drawn steel pipe Vinyl pipe 0.92 0.85 0.82 0.8
Circular pipe section pressure loss
∆p = λ
·· ·
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
Page 49
Duct
No.
section
Outline diagram
Conditions
C
value
12 Transformer 0.15 9D
Abrupt
13
Entrance
0.50 30D
Abrupt
14
Exit
1.0 60D
Bellmouth
15
Entrance
0.03 2D
Bellmouth
16
Exit
1.0 60D
Re-entrant
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
Abrupt
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
Abrupt
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
43
CHAPTER 4 ● Characteristics
(3) How to calculate curved sections
Table 6 List of pressure losses in each duct section
Length of
equivalent
circular
pipe
No. of vanes
With or without vanes, rectangular or circular
1/2 times value for similar 90°
Length of
equivalent
circular
pipe
Free are ratio
14° or less
D
Duct
No.
section
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
Square 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
Page 50
High notch air volume at 60 Hz
44
CHAPTER 4 ● Characteristics

3. How to Obtain Efficiency from Characteristic Curves

3.1 Commercial-use Lossnay
How to read Commercial-use Lossnay characteristic curve
●
Obtaining the efficiency when supply air and exhaust air volumes differ The efficiency obtained from the intake side air value in each characteristic curve can be corrected with the air volume ratio in the chart on the right. If the intake side and exhaust side duct lengths differ greatly or if a differential air volume is required, obtain the intake side efficiency from the chart on the right.
3.2 Building-use Lossnay
How to read LU type Lossnay characteristic curves
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(%)
Heatrecovery
efficiency
(%)
Airvolumeratio=
Exhaustairvolume Supplyairvolume
Correctedheatrecoveryefficiency(%)
Heatrecovery efficiency whenexhaust airvolumeand supplyairvolume arethesame
7
1
Staticpressure lossonsupply side
4
Staticpressure losson exhaustside
5
Airvolumeratio=
Exhaustairvolume Supplyairvolume
Efficiencycorrectioncurve
6
Requiredairvolumeonexhaustside
Requiredairvolumeonsupplyside
Heatrecoveryefficiency onsupplysidewhen exhaustairvolumeand supplyairvolumediffer
7
2
3
Staticpressureinsideunit
Temperaturerecoveryefficiency
Enthalpy
recovery
efficiency(heating)
Enthalpy
recovery
efficiency(cooling)
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 at 60 Hz
Total static pressure loss (or total straight pipe equivalent length)
Static pressure outside unit
At 50 Hz, equivalent to 60 Hz at dotted line
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
Heat recovery efficiency correction curve
Page 51
45
CHAPTER 4 ● Characteristics

4. Sound

Sound is emitted when any object is excited causing it to vibrate. The object that vibrates is called the sound source, and the energy that is generated at the source is transmitted through the air to the human ear. Humans can hear the sound only when the ear drum vibrates.
4.1 Sound level and auditory perception
Sound level is the sound wave energy that passes through a unit area in a unit time, and is expressed in dB (decibel) units. The sound heard by the human ear differs according to the strength of the sound and the frequency, and the relation to the pure tone sound is as shown on the right. The vertical line shows the strength of the sound and the horizontal line shows the frequency. For frequencies between 20 Hz to 15,000 Hz which can be felt by the human ear, the strength of sound that can be felt that is equivalent to a 1,000 Hz sound is obtained for each frequency. The point where these points cross is the sound level curve, and a sound pressure level numerical value of 1,000 Hz is expressed. These are called units of phons. For example, the point on the 60 curve is perceived as 60 phons.
●
On average, the human senses a sound that is less than 1,000 Hz as rather weak, and a sound between 2,000 to 5,000 Hz as strong.
4.2 How to measure sound levels
A sound level meter (JIS C 1502, IEC 651) is used to measure sound levels. This sound level meter has three characteristics (A, B and C characteristics) as shown on the right. These represent various sound wave characteristics. Generally, the A characteristic, which is the most similar to the human ear, is used.
Sound level (dB)
Frequency (Hz)
Minimum audible valve
120 dB
100
–200
–20
–2
–0.2
–0.02
–0.002
–0.0002
80
60
40
20
4.2
Response (dB)
Frequency (Hz)
C characteristic
B characteristic
A characteristic
Sound
presure
(Microbar)
Sound
strength
(W / cm
2
)
ISO audio perception curve
Page 52
46
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
Theatre (approx. 500 seats) 35 20 - 25 Library 40 30
Classroom 40 25 Small office 45 30 - 35
Conference room 40 25 Restaurant 50 45
Apartment 40 25 - 30 Gymnasium 55 50
Hotel 40 25 - 30 Large conference room 50 45
Housing (room) 40 25 - 30 Factory 70 50 or more
4.3 Frequency analysis of sound
It is said that the human ear senses differently according to the frequency. However, the sound generated from a vibration is not limited to one frequency, but instead, various frequencies are generated at differing levels. This is expressed by the NC curve, which is determined according to the difficulty of hearing a conversation.
●
Even if the sound is a very low level, it is annoying if a specific frequency is emitted very loudly. These sounds are suppressed to a minimum during product design stages, but, the sound may become very disturbing with resonance of the ceiling, wall, etc.
Example Continuous frequency analysis NC curve
●
Tolerable noise levels and NC values according to room application
Frequency band (Hz)
Level (dB)
Frequency (Hz)
SPL (dB)
Min. audible limit
Page 53
47
CHAPTER 4 ● Characteristics
* Approximate values of noise levels using practical examples
The following diagram shows noises found near us. Approximate degree of noise levels can be seen with these examples.
* Noise levels and perception
Boiler making Forginb, rivetting, rock drilling
Crusher
Engine, large motor
Noisy factory
Normal machine factory
(dB) (Perception at site)
130 Painful to ear 120 Near airplane engine
110 Slight pain to ear Automobile horn
(2 m away)
100 Want to cover ear Train with open
window in tunnel
90 Conversation with Train passing on
person in front of you overhead tracks is 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 always audible Among quiet group
and is disturbing of pedestrians
40 Quiet but not relaxing In quiet group of
persons
30 Relaxing In broadcasting studio
20 Dead quiet Sound of leaves
brushing against
10 each other
0
Source: “Heibon Sha, industrial Encyclopedia”
Computer room
Typing room
Many people
Few people
Subway
Overhead train
Passenger car
Business and industrial district
Suburb
Quiet night
Factory
Tr ansportation facilities
Conversation
Housing district
Office
Page 54
4.4 Indoor noise
(1) Principle of indoor noise
1) Power levels The Power level (PWL) of the sound source must be
understood when considering noise effects. The following formula is used to obtain PWL from the measured sound pressure data (values noted in catalog) in an anechoic chamber.
PWL = SPLo + 20 logro + 11 [dB]. . . . . . . . . . . . . . . . . . . . . (I)
PWL : Sound source power level (dB)
SPLo : Measured sound pressure in anechoic
chamber (dB)
ro : Measurement distance (m)
2) Principal model Consider the room shown in Figs. 1 and 2.
●
Fig. 1 shows an example of the integrated main unit and supply air diffuser (and return grille). This is equivalent to the cassette-type Lossnay. Fig. 2 shows an example of a separated main unit and supply air diffuser (and return grille). This is equivalent to the ceiling embedded-type Lossnay.
●
is the direct sound from the supply air diffuser (return
grille) and is the echo sound. ( to ) is the direct sound that is emitted from the main unit and duct and passes through the finished ceiling and leaks. is the echo sound of .
3) Setting of noise
●
The following formula is used to obtain the noise value at a position in the room.
SPL [dB] = PWL + 10 log + ........................(II)
(i) (ii)
SPL :
Sound pressure level at reception point [dB]
PWL : Sound source power level [dB]
Q:Directivity factor (Refer to Fig. 3)
r:Distance from sound source [m] R:Room constant [R = αS/(1 – α)] α :Average sound absorption ratio in room
(Normally, 0.1 to 0.2)
S:Total surface area in room [m
2
]
48
CHAPTER 4 ● Characteristics
Sound source position
Centre of room
Centre of ceiling
Edge
Corner
a
b
c
d
Q
1
2
4
8
Fig. 1
Fig. 2
Fig. 3
(Sound source position and directivity factor Q)
3
1
Q
4πr
2
4
R
{}
Main unit
r
o
Supply air diffuser (return grille)
Supply air diffuser (return grille)
c
b
a
d
Main unit
Page 55
49
CHAPTER 4 ● Characteristics
●
For the supply air diffuser (and return grille) in Fig. 2, PWL must be corrected for the noise alternation provided by the duct work (TL) such that:
PWL’ = PWL – TL
●
Item i in formula (II) is the direct sound ( , ), and ii is the echo sound ( , ).
●
The number of sound sources in the room (main unit, supply air diffuser, return grille etc.) is obtained by calculating formula (II), and combining the number with formula (III).
SPL = 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 frequwncy band, and is combined with formula (III) for an accurate value.
(2) Avoiding noise disturbance from
Lossnay unit
1) When unit air passage behind ceiling is sound source (Fig. 1 , , Fig. 2 to , )
(A) Avoid the following types of construction when disturbing
noise may be emitted from large units. (Refer to Fig. 4) a) Sudden contraction of duct diameter
(Ex. ø 250 → ø 150, ø 200 → ø 100)
b) Sudden curves in aluminum flexible ducts, etc.
(Especially right after unit outlet) c) Opening in ceiling plates d) Suspension on weak material
(B) The following countermeasures should be taken.
(Refer to Fig. 5) a) Use ceiling material with high soundproofing
properties (high transmission loss). (Care is required
for low frequency components as the difference in
material is great). b) Addition of soundproofing material to areas below
sound source.
(The entire surface must be covered when using
soundproofing sheets. Note, that in some cases,
covering of the area around the unit may not be
possible due to the heat generated from the unit.)
125
250
500
1,000
2,000
4,000
Material ( )
indicates
thickness (mm)
Lauan
plywood (12)
23
20
21
23
26
24
—
Fig. 4
Fig. 5
Transmission loss in ceiling material (dB) Example
Average
20
10
11
19
26
34
42
22
12
15
21
28
35
39
Plaster
board (7)
Plaster
board (9)
Frequency band (Hz)
1
3
a) d)
a) b)
c) b)
Page 56
50
CHAPTER 4 ● Characteristics
2)
When supply air diffuser (and return grille) is sound source
..... part 1
(A) If the main unit is separated from the supply air diffuser
(and return grille) as shown in Fig. 6, the use of a silencer box a), silence duct b) or silence grille c) is recommended.
(B) If a draft sound is being emitted from the supply air
diffuser (and return grille), branch the flow as shown in Fig. 7 a), lower the flow velocity with a grille, and add a silencer duct to section b). (If the length is the same, a silencer duct with the small diameter is more effective.)
3)
When supply air diffuser (and return grille) is sound source
..... part 2
(A) If the main unit and supply air diffuser (and return grille)
are integrated as shown in Fig. 8, or if the measures taken in 2) a) and b) are inadequate, the interior material in the room can be changed to that having a high sound absorbency as shown in Fig. 8 a). This is not, however, very effective towards direct sounds.
(B) Installing the sound source in the corner of the room as
shown in Fig. 8 b) is effective towards the center of the room, but will be inadequate towards people in the corner of the room.
Fig. 6
Fig. 7
Fig. 8
a) b) c)
a) b)
a) b)
Page 57
51
CHAPTER 4 ● Characteristics

5. NC Curves (LGH-RX4 Series)

● Ceiling embedded-type
LGH-15RX4
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 : 240 V 50 Hz Power supply : 220 V 60 Hz
90
85
80
75
70
65
60
55
50
45
40
35
30
25
20
15
10
62.5 125 500250 1000 2000 4000 8000
Overall
Octave band frequency near center (Hz)
Octave band sound pressure level (dB)
90
85
80
75
70
65
60
55
50
45
40
35
30
25
20
15
10
62.5 125 500250 1000 2000 4000 8000
Overall
Octave band frequency near center (Hz)
Octave band sound pressure level (dB)
NC-70
NC-60
NC-50
NC-40
NC-30
NC-20
NC-10
NC-70
NC-60
NC-50
NC-40
NC-30
NC-20
NC-10
1.5 m below
Measurement point
1.5 m below
Measurement point
Low
High
Extra high
Low
High
Extra
high
LGH-25RX4
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 : 240 V 50 Hz Power supply : 220 V 60 Hz
LGH-35RX4
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 : 240 V 50 Hz Power supply : 220 V 60 Hz
90
85
80
75
70
65
60
55
50
45
40
35
30
25
20
15
10
62.5 125 500250 1000 2000 4000 8000
Overall
Octave band frequency near center (Hz)
Octave band sound pressure level (dB)
90
85
80
75
70
65
60
55
50
45
40
35
30
25
20
15
10
62.5 125 500250 1000 2000 4000 8000
Overall
Octave band frequency near center (Hz)
Octave band sound pressure level (dB)
NC-70
NC-60
NC-50
NC-40
NC-30
NC-20
NC-10
NC-70
NC-60
NC-50
NC-40
NC-30
NC-20
NC-10
Low
High
Extra
high
Low
High
Extra high
1.5 m below
Measurement point
1.5 m below
Measurement point
90
85
80
75
70
65
60
55
50
45
40
35
30
25
20
15
10
62.5 125 500250 1000 2000 4000 8000
Overall
Octave band frequency near center (Hz)
Octave band sound pressure level (dB)
90
85
80
75
70
65
60
55
50
45
40
35
30
25
20
15
10
62.5 125 500250 1000 2000 4000 8000
Overall
Octave band frequency near center (Hz)
Octave band sound pressure level (dB)
NC-70
NC-60
NC-50
NC-40
NC-30
NC-20
NC-10
NC-70
NC-60
NC-50
NC-40
NC-30
NC-20
NC-10
High
Extra
high
Low
High
Extra high
Low
1.5 m below
Measurement point
1.5 m below
Measurement point
Page 58
52
CHAPTER 4 ● Characteristics
90
85
80
75
70
65
60
55
50
45
40
35
30
25
20
15
10
62.5 125 500250 1000 2000 4000 8000
Overall
Octave band frequency near center (Hz)
Octave band sound pressure level (dB)
90
85
80
75
70
65
60
55
50
45
40
35
30
25
20
15
10
62.5 125 500250 1000 2000 4000 8000
Overall
Octave band frequency near center (Hz)
Octave band sound pressure level (dB)
NC-70
NC-60
NC-50
NC-40
NC-30
NC-20
NC-10
NC-70
NC-60
NC-50
NC-40
NC-30
NC-20
NC-10
High
Extra high
Low
High
Extra high
Low
1.5 m below
Measurement point
1.5 m below
Measurement point
90
85
80
75
70
65
60
55
50
45
40
35
30
25
20
15
10
62.5 125 500250 1000 2000 4000 8000
Overall
Octave band frequency near center (Hz)
Octave band sound pressure level (dB)
90
85
80
75
70
65
60
55
50
45
40
35
30
25
20
15
10
62.5 125 500250 1000 2000 4000 8000
Overall
Octave band frequency near center (Hz)
Octave band sound pressure level (dB)
NC-70
NC-60
NC-50
NC-40
NC-30
NC-20
NC-10
NC-70
NC-60
NC-50
NC-40
NC-30
NC-20
NC-10
Low
High
Extra
high
Low
High
Extra high
1.5 m below
Measurement point
1.5 m below
Measurement point
LGH-50RX4
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 : 240 V 50 Hz Power supply : 220 V 60 Hz
LGH-65RX4
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 : 240 V 50 Hz Power supply : 220 V 60 Hz
LGH-80RX4
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 : 240 V 50 Hz Power supply : 220 V 60 Hz
90
85
80
75
70
65
60
55
50
45
40
35
30
25
20
15
10
62.5 125 500250 1000 2000 4000 8000
Overall
Octave band frequency near center (Hz)
Octave band sound pressure level (dB)
90
85
80
75
70
65
60
55
50
45
40
35
30
25
20
15
10
62.5 125 500250 1000 2000 4000 8000
Overall
Octave band frequency near center (Hz)
Octave band sound pressure level (dB)
NC-70
NC-60
NC-50
NC-40
NC-30
NC-20
NC-10
NC-70
NC-60
NC-50
NC-40
NC-30
NC-20
NC-10
High
Extra
high
Low
High
Extra high
Low
1.5 m below
Measurement point
1.5 m below
Measurement point
Page 59
53
CHAPTER 4 ● Characteristics
90
85
80
75
70
65
60
55
50
45
40
35
30
25
20
15
10
62.5 125 500250 1000 2000 4000 8000
Overall
Octave band frequency near center (Hz)
Octave band sound pressure level (dB)
90
85
80
75
70
65
60
55
50
45
40
35
30
25
20
15
10
62.5 125 500250 1000 2000 4000 8000
Overall
Octave band frequency near center (Hz)
Octave band sound pressure level (dB)
NC-70
NC-60
NC-50
NC-40
NC-30
NC-20
NC-10
NC-70
NC-60
NC-50
NC-40
NC-30
NC-20
NC-10
Low
High
Extra
high
Low
High
Extra
high
1.5 m below
Measurement point
1.5 m below
Measurement point
90
85
80
75
70
65
60
55
50
45
40
35
30
25
20
15
10
62.5 125 500250 1000 2000 4000 8000
Overall
Octave band frequency near center (Hz)
Octave band sound pressure level (dB)
90
85
80
75
70
65
60
55
50
45
40
35
30
25
20
15
10
62.5 125 500250 1000 2000 4000 8000
Overall
Octave band frequency near center (Hz)
Octave band sound pressure level (dB)
NC-70
NC-60
NC-50
NC-40
NC-30
NC-20
NC-10
NC-70
NC-60
NC-50
NC-40
NC-30
NC-20
NC-10
Low
High
Extra
high
High
Extra high
Low
1.5 m below
Measurement point
1.5 m below
Measurement point
90
85
80
75
70
65
60
55
50
45
40
35
30
25
20
15
10
62.5 125 500250 1000 2000 4000 8000
Overall
Octave band frequency near center (Hz)
Octave band sound pressure level (dB)
90
85
80
75
70
65
60
55
50
45
40
35
30
25
20
15
10
62.5 125 500250 1000 2000 4000 8000
Overall
Octave band frequency near center (Hz)
Octave band sound pressure level (dB)
NC-70
NC-60
NC-50
NC-40
NC-30
NC-20
NC-10
NC-70
NC-60
NC-50
NC-40
NC-30
NC-20
NC-10
1.5 m below
Measurement point
1.5 m below
Measurement point
High
Extra
high
Low
High
Extra high
Low
LGH-100RX4
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 : 240 V 50 Hz Power supply : 220 V 60 Hz
LGH-200RX4
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 : 240 V 50 Hz Power supply : 220 V 60 Hz
LGH-150RX4
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 : 240 V 50 Hz Power supply : 220 V 60 Hz
Page 60
54
CHAPTER 4 ● Characteristics
Blades
Model
LGH-15RX
4
LGH-25RX4
LGH-35RX4
LGH-50RX4LGH-65RX4
LGH-80RX4
LGH-100RX4
LGH-150RX4
LGH-200RX4
LGH-40ES
Material
Shape,
diameter
PP resin
Centrifugal fan
ø180
PP resin
Centrifugal fan
ø180
PP resin
Centrifugal fan
ø220
PP resin
Centrifugal fan
ø220
PP resin
Centrifugal fan
ø245
PP resin
Centrifugal fan
ø245
PP resin
Centrifugal fan
ø245
PP resin
Centrifugal fan
ø245
PP resin
Centrifugal fan
ø245
PP resin
Centrifugal fan
ø200
Material
Prefilter
NP/400
Prefilter
NP/400
Prefilter
NP/400
Prefilter
NP/400
Prefilter
NP/400
Prefilter
NP/400
Prefilter
NP/400
Prefilter
NP/400
Prefilter
NP/400
Prefilter
NP/400
Dimensions
549
×
125
×
15
653
×
151
×
15
784
×
178
×
15
926
×
178
×
15
852
×
213
×
15
880
×
238
×
15
1,117 × 238 × 15
890
×
238
×
15
1,117 × 238 × 15
750 × 160 × 15
Filtering
efficiency /class
Gravitational
method 82% / EU3
Gravitational
method 82% / EU3
Gravitational
method 82% / EU3
Gravitational
method 82% / EU3
Gravitational
method 82% / EU3
Gravitational
method 82% / EU3
Gravitational
method 82% / EU3
Gravitational
method 82% / EU3
Gravitational
method 82% / EU3
Gravitational
method 82% / EU3
Material
Self-extinguishing
urethane foam
Self-extinguishing
urethane foam
Self-extinguishing
urethane foam
Self-extinguishing
urethane foam
Self-extinguishing
urethane foam
Self-extinguishing
urethane foam
Self-extinguishing
urethane foam
Self-extinguishing
urethane foam
Self-extinguishing
urethane foam
Self-extinguishing
urethane foam
Ambient
temperature
-10°C to +40°C
RH80% or less
-10°C to +40°C
RH80% or less
-10°C to +40°C
RH80% or less
-10°C to +40°C
RH80% or less
-10°C to +40°C
RH80% or less
-10°C to +40°C
RH80% or less
-10°C to +40°C
RH80% or less
-10°C to +40°C
RH80% or less
-10°C to +40°C
RH80% or less
-10°C to +40°C
RH80% or less
Exhaust air
conditions (RA)
-10°C to +40°C
RH80% or less
-10°C to +40°C
RH80% or less
-10°C to +40°C
RH80% or less
-10°C to +40°C
RH80% or less
-10°C to +40°C
RH80% or less
-10°C to +40°C
RH80% or less
-10°C to +40°C
RH80% or less
-10°C to +40°C
RH80% or less
-10°C to +40°C
RH80% or less
-10°C to +40°C
RH80% or less
Supply air
conditions (OA)
-10(-15)°C to +40°C
RH80% or less
-10(-15)°C to +40°C
RH80% or less
-10(-15)°C to +40°C
RH80% or less
-10(-15)°C to +40°C
RH80% or less
-10(-15)°C to +40°C
RH80% or less
-10(-15)°C to +40°C
RH80% or less
-10(-15)°C to +40°C
RH80% or less
-10(-15)°C to +40°C
RH80% or less
-10(-15)°C to +40°C
RH80% or less
-10°C to +40°C
RH80% or less
Q’ty
2
2
2
2
2
2
2
4
4
2
Filter
Insulation material
Product usage conditions

6. List of Models

6.1 List of material colours for Lossnay
Product usage conditions
(Ambient temperature, exhaust
air, supply air conditions)
Model
LU-500
Colour Munsell
symbol
5Y 6.5/1
Mitsubishi
colour No.
N-E6
Material
Steel plate
Thickness: 1.6 t
Paint
specification
Polyester
powder
Material
Incombustible
treated paper
Weight with
frame/unit
22 kg
Q’ty
4
Material
Self-extinguishing
urethane foam
-10°C to +50°C RH80%
or less
Insulation materialHeat recovery coreOutsideColour
Dimensions
without frame
550 × 487
Page 61
55
CHAPTER 4 ● Characteristics
6.2 List of industrial/business Lossnay accessories
Model
LGH-15RX
4
LGH-25RX4
LGH-35RX4
LGH-50RX4
LGH-65RX4
LGH-80RX4
LGH-100RX
4
LGH-150RX4
LGH-200RX4
LGH-40ES
LU-500
Accessories
● Duct connection flanges . . . . . . . . × 4
● Mounting screws . . . . . . . . . . . . . × 18
● Protective cover . . . . . . . . . . . . . . × 1 <For installing upside down>
● Slim-Lossnay connection cable . . × 1 (gray : two wires)
● IB . . . . . . . . . . . × 1
● IM . . . . . . . . . . . × 1
●
Mounting screws . . . . . . . . . . . . . × 16
●
Duct connection flange . . . . . . . . . × 4
● Slim-Lossnay connection cable . . × 1 (gray : two wires)
● IB . . . . . . . . . . . × 1
● IM . . . . . . . . . . . × 1
● IB . . . . . . . . . . . × 1
● IM . . . . . . . . . . . × 1
● IB . . . . . . . . . . . × 1
Duct packaging site
EA RA
OA SA
SA
*Top view.
2 are inserted on top of each other at the SA and EA openings, in the opposite direction.
2 are inserted in each SA opening of both the top and bottom units.
—
—
Page 62
Page 63

CHAPTER 5
System Design Recommendations

Page 64
58
CHAPTER 5 ● System Design Recommendations

1. Lossnay Usage Conditions

Main unit installation conditions Outdoor air and exhaust air conditions
Commercial-use Lossnay -10°C to +40°C, RH80% or less -10°C to + 40°C, RH80% or less.
Facility Lossnay LU model Lossnays -10°C to +50°C, RH80% or less Same as left
In some cases special attention needs to be paid to extreme operating conditions. These are described as below:
1.1 Use in cold climates (outdoor temperature: –5°C or less)
Plot the Lossnay intake air conditions A and B on a psychrometric chart as shown on the right. If the high temperature side air B intersects the saturation curve such as at C, moisture condensation or frosting will occur on the Lossnay. In this case, the low temperature side air A should be preheated to the temperature indicated by point A’ so that point C shifts to the point C’. The LGH-RX more information about heater model selection and wiring method, please refer to the Control volume (Technical manual (Controls) page 40).
4 type has a built-in preheater control circuit. For
Saturation curve
C
A
Dry bulb temperature (°C)
C’
A’
B
Absolute humidity (kg/kg’)
1.2 Use in high humidity conditions (Relative humidity: 80% or more)
When using the system in high humidity conditions such as heated pools, bathrooms, mushroom cultivation houses, etc., moisture will condense inside the Core, and drainage will occur. In these cases, the general purpose Lossnay that uses treated paper cannot be used. Instead the moisture resistant Lossnay must be used. The following moisture resistant Lossnay models are available. The usage conditions differ so select the model according to the application.
1.3 Use in other special conditions
●
Avoid using Lossnay under air condition with acid, alkalis, organic solvent, oil mist, paint, or harmful gas as presticide, corrosive gas, etc.
●
Rust, fire or malfunction may occur by brine and hotspring steam.
Installing Brine Damage Resistant Filters inside outdoor air duct if the Lossnay operates in the briny air.
●
Outdoor air or mist may flow through the duct into your room when Lossnay is in off-mode at windy and foggy area.
To prevent sucking of outdoor air or fog, electric damper is advised to be installed.
●
Use where heat is recovered from odor-laid air and supplied to another place (area) is not possible.
Page 65
59
CHAPTER 5 ● System Design Recommendations

2. Lossnay LGH series noise level

The noise level specified for Lossnay units is as that measured in an anechoic chamber. The sound level may increase by 8 to 11 dB according to the installation construction material, and room contents, by noise reflection. When using the Lossnay in a quiet room, it is recommended that measures such as installing a muffling duct be carried out.

3. Attachment of Air Filter

An air filter must be mounted to the air inlets (both intake and exhaust) of the Lossnay to clean the air and to prevent the Core from clogging. Always mount this filter, and periodically service it.

4. Duct Construction

●
Always cover the two ducts on the outdoor side (outdoor air intake and exhaust outlet) with insulation to prevent frost or condensation.
●
The outdoor duct gradient must be 3.3% or more (to wall side) to prevent rain water from rain water running towards the Lossnay. (Refer to page 86).
●
Do not use the standard vent caps or round hoods where they may come into direct contact with rain water. (Instead, use of a deep hood is recommended.)

5. By-pass Ventilation

Do not operate with “By-pass ventilation” when heating during winter. Frost or condensation may form on the main unit and cause discolouring of the ceiling, etc.
Page 66

6. Transmission Rate of Various Gases and Related Maximum Workplace Concentration

60
CHAPTER 5 ● System Design Recommendations
Measurement
Air volume Exhaust air
Supply air
Transmission
Max. workplace
conditions
Gas ratio concentration concentration rate concentrations
Q
SA/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
Sulfulic acid 1.0 2.6 mg/m
3
- 0 mg/m
3
- 0 0.25
Trichlene 1.0 85 1.36 1.6 200
Acetone 1.0 5 0.04 0.8 1,000
Xylene 1.0 313 <5.0 <1.6 150
Isopropyl alcohol 1.0 3,000 <25 <0.8 400
Methanol 1.0 41 0.49 1.2 200
Ethanol 1.0 35 0.49 1.4 1,000
Ethyl acetate
1.0 25 0.28 1.1 400
alcohol
Ammonia 1.0 290 7.25 2.5 50
Hydrogen sulfide 1.0 15 0.24 1.6 10
Carbon monoxide 1.0 71.2 0.43 0.6
Carbon dioxide 1.0 37,800 600 0.3
Smoke 1.0 – – 1 - 2
Formaldehyde 1.0 32 0.3 0.9 0.08
Sulfur hexaflouride 1.0 116 0.8 0.7
Skatole 1.0 27.1 0.56 2.0
Indole 1.0 27.1 0.56 2.0
Toluene 1.0 6.0 0.1 1.7
Measurement method
• Chemical analysis with colorimetric method for H2SO4
• 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, 85% RH
* OA density for
CO
2
is 500 ppm.
CAUTION
The above does not apply to the moisture resistant total heat recovery unit.
Page 67
Main Molecular Gas Sulubility Max.
generation Gas name formula vapour
Non-toxic/
in water workplace
Useability
site mist odor
toxic/
concentration
of Lossnay
m /m
g/100g
Sulfuric acid H
2SO4 Mist Found 2,380 0.25
×
Nitric acid HNO
3 Mist Found 180 10
×
Phosphoric acid H
3PO4 Mist Found 41 0.1
×
Acetic acid CH
3COOH Mist Bad odor 2,115 25
×
Chemical
Hydrogen chloride HCl Gas Found 427 58 5
×
plantor
Hydrogen fluoride HF Gas Found 90 0.6
×
chemical
Sulfur dioxide SO
2 Gas Found 32.8 0.25
laboratory
Hydrogen sulfide H
2S Gas Found 2.3 10
Ammonia NH
3 Gas Bad odor 635 40 50
×
Phosphine PH
3 Gas Found 0.26 0.1
Methanol CH
3OH Vapor Found Soluble 200
Ethanol CH
3CH2OH Vapor Found Soluble 1,000
Ketone Vapor Found Soluble 1,000
Skatole C
9H9N Gas Bad odor Minute
Toilet 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 None 0.0167
Air
Oxygen O
2 Gas None 0.0283
(reference)
Nitrogen N
2 Gas None 0.0143
Carbon monoxide CO Gas Found 0.0214
Carbon dioxide CO
2 Gas None 0.759
RR
61
CHAPTER 5 ● System Design Recommendations

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

Note: 1. Water soluble gases and mists cannot be used because the amount that is transmitted with the water is too great.
2. Acidic gases and mists cannot be used because these will accumulate in the Core and cause damage.
3. The above does not apply to the moisture resistant total heat recovery unit.
Page 68
62
CHAPTER 5 ● System Design Recommendations
8.

Positioning of the Supply/Exhaust Fans and the Air Transmission Rate (excluding moisture resistant total heat recovery units) (only for LU type)

The following four methods can be used for when setting the Lossnay supply and exhaust fans around the Lossnay Core. When using the LU models, methods a or b should be used in respect of both the Lossnay Core air leakage and effective air ventilation. Use method c if air leakage to the RA or SA sides is not allowed such as in hospital air conditioning, or transmission of the fan noise into the room must be suppressed by putting the Lossnay Core between the supply/exhaust fans and room, and if a certain degree of air leakage is allowed between OA to EA.
a. Installing the supply fan (OA-SA) and exhaust fan b. Installing the supply fan (OA-SA) and exhaust fan
(RA-EA) for suction feed to the Lossnay Core (RA-EA) for forced supply to the Lossnay Core
If the static pressure difference between SA and RA and The air leakage rate is the same as in system a. between EA and OA is 50mmAq, the air leakage rate will be 2.5%, and 3.4%. This value is of no problem for most standard uses.
c. Installing the supply fan (OA-SA) for force feed and d. Installing the supply fan (OA-SA) for suction feed
the exhaust fan (RA-EA) for suction feed and the exhaust fan (RA-EA) for force feed
Lossnay
EA
OA RA
SA
Lossnay
EA
OA RA
SA
In this case, the positive/negative relation of the static In this case, the intake side pressure (OA-SA) will be pressure will be the reverse of that in system d, and the air negative, and the exhaust side pressure (RA-EA) will be leakage outside the room (leakage from OA to EA) will be positive, so the amount of air leakage to the intake side will the same as system d. Thus, the effective volume of be the greatest. If the static pressure difference between ventilating air will be reduced by that rate. OA and RA is 50 mmAq, the air leakage rate will be 10.5%,
and 13.0%. This system can be used when an air leakage of 10% to the intake side (OA-SA) is permitted, but should be avoided in all other cases.
Lossnay
EA
RA
OA
SA
Lossnay
EA
RA
OA
SA
Outdoors
Fan for exhaust air Fan for supply air
Indoors
Outdoors
Fan for exhaust air
Fan for supply air
Indoors Outdoors
Fan for supply air
Fan for exhaust air
Indoors
Outdoors
Fan for supply air Fan for exhaust air
Indoors
Page 69
63
CHAPTER 5 ● System Design Recommendations

9. Combined Operation with other Air Conditioners (Refer to technical manual (Control) in detail)

Connecting the Lossnay can configure the following system.
Interlocked with City Multi
Interlocked with Mr. Slim
Independent Lossnay Unit (Not interlocked with City Multi or Mr. Slim systems.)
Interlocked with external unit (BMS)
City Multi
indoor unit
Remote controller
M-NET transmission cable
Lossnay unit
LGH-**RX
4-E
Mr.Slim (A, K-control)
indoor unit
Lossnay unit
LGH-**RX
4-E
Lossnay remote controller cannot be used.
Remote controller
Slim-Lossnay connecting cable (Enclosed accessory)
Lossnay remote controller
M-NET transmission cable
Power supply unit
Lossnay unit
LGH-**RX
4-E
Lossnay unit LGH-**RX
4-E
EXT. signal source
for interlocking to the Lossnay
Page 70
64
CHAPTER 5 ● System Design Recommendations
10. Automatic Ventilation Switching (Refer to technical manual (Control) page 38)
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 troublesome switch operations when setting the Lossnay ventilator to “By-pass” ventilation. The following shows the effect “By-pass” 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), “By-pass” 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 people in a room cause the temperature of the room to rise, “By-pass” ventilation draw in the cool outside air and use it as is to cool the room.
(3) Night purge
“By-pass” ventilation can be used to release hot air from inside the building that has accumulated in buildings a business district during the hot summer season.
(4) Office equipment room cooling
During cold season, outdoor air can be drawn in and used as is to cool rooms where the temperature has risen due to the use of office equipment. (Only when interlocked with City Multi and Mr. Slim indoor unit)
Page 71
Model name Installation patterns
LGH-15RX
4
LGH-25RX4
LGH-35RX4 LGH-50RX4 LGH-65RX4 LGH-80RX4 LGH-100RX4
SA OA
OA EA
EA OA
RA SA
SA
RA
OA
EA
SA
RA
OA
EA
65
CHAPTER 5 ● System Design Recommendations

11. Vertical Installation of LGH Series

Installation of ceiling embedded-type industrial Lossnay
11.1 Top/bottom reverse installation
All LGH-RX4 models can be installed in reverse.
11.2 Vertical installation
Vertical installation is possible, but the installation pattern is limited for some models. Refer to the following table for the installation patterns.
To p
Bottom
To p
Bottom
To p
Bottom
To p
Bottom
To p
Bottom
Bottom
To p
(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.)
11.3 Slanted installation
Slanted installation is not possible.
Special note
The LGH-RX
4 model was conventionally designed for being embedded in the ceiling. If possible, vertical installation should be
avoided in regard to construction and maintenance.
Page 72
66
CHAPTER 5 ● System Design Recommendations
12. Installation of Supplementary Fan Devices After Lossnay
Unit
On occasions it may be necessary to install additional fans in the ductwork following the LGH type Lossnay. This is because of the inclusion 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 care should be taken to avoid undue stress on the fan motors. Referring to the diagrams below, Lossnay with extra fan 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
+ H2
Q
1
Q1 Q1’
Q
Lossnay with static pressure increasing component.
Lossnay with static pressure increasing component.
Lossnay
Q
Q
A
Page 73

CHAPTER 6
Examples of Lossnay Applications

Page 74
68
CHAPTER 6 ● Examples of Lossnay Applications
Lossnay ventilation systems are proposed for eight types of applications in this chapter. These systems are planned for Japanese use, and actual systems will differ according to each country. These should be used only as reference.

1. Large Office Building

1.1 System plan points
Conventional central systems in large buildings, run in floor and building ducts, have generally been preferred to individual room units. Thus, air conditioning and ventilation after working hours was not possible. In this plan, an independent dispersed ventilation method has been applied to resolve this problem. Such a system’s main advantage is that it allows 24-hour operation. A package-type air conditioning unit is installed in the ceiling, and ventilation is performed with the ceiling-embedded-type Lossnay. Ventilation in the toilet, kitchenette and lift halls, etc., is performed with a straight centrifugal fan.
Setting outline
●
Building form : Basement floor SRC (Slab Reinforced Concrete), 8 floors above ground S construction
Total floor space 30,350 m
2
●
Basement : Employee cafeteria
●
Ground floor : Lobby, conference room
●
2 to 7th floor : Offices, salons, board room
●
Air conditioning : Package air conditioning
●
Ventilation : Ceiling embedded-type Lossnay, straight centrifugal fan
1.2 Current topics
(1) Operation system that answers individual needs is required.
●
Free independent operation system
●
Simple control
(2) Effective use of floor space
(elimination of machine room)
(3) Application to Building Management Laws
●
Effective humidification
●
Elimination of indoor dust
(4) Energy conservation
1.3 Proposed details
(1) Air conditioning
●
In general offices, the duct method will be applied with several ceiling-embedded multiple cooling heat pump packages in each zone to allow total zone operation.
●
Board rooms, conference rooms and salons will be air conditioned with a ceiling embedded-type or cassette-type multiple cooling heat pump package in each room.
Installation state of office system air conditioning system – The air supplied from the Lossnay is introduced into the intake side of the air conditioner, and the room stale air is directly removed from the inside of the ceiling.
Return grille
Grille
SA (Supply air)
Air conditioner
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
Page 75
69
CHAPTER 6 ● Examples of Lossnay Applications
(2) Ventilation
●
For general offices, a ceiling embedded-type Lossnay will be installed in the ceiling. The inside of the ceiling will be used as a return chamber for exhaust, and the air from the Lossnay will be supplied to the air-conditioning return duct and mixed with the air in the air conditioning passage. (Exhaust air is taken in from the entire area, and supply air is introduced into the air conditioner to increase the ventilation effectiveness for large rooms.)
●
For board rooms, conference rooms and salons, a ceiling embedded-type Lossnay will be installed in the ceiling. The stale air will be duct exhausted from the discharge grille installed in the centre of the ceiling. The supply air will be discharged into the ceiling, where after mixing with the return air from the air conditioner it is supplied to the air conditioner.
●
The air in the toilet, kitchenette, and lift hall, etc., will be exhausted with a straight centrifugal fan in each room. The OA supply for this section will use the air supplied from the Lossnay. (The OA volume will be obtained by setting the Lossnay supply fan in the general office to the extra-high notch.)
Installation state of air conditioning system for board rooms, conference rooms, salons - the air supplied from the Lossnay is blown into the ceiling, and the stale air is 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
Page 76
70
CHAPTER 6 ● Examples of Lossnay Applications
●
A gallery will be constructed on the outer wall for the outer wall exhaust air outlets to allow for blending in with the exterior.
Reference floor 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 room
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 room
Machine room
Office
Office
Page 77
71
CHAPTER 6 ● Examples of Lossnay Applications
(3) Humidification
If the load fluctuation of the required humidification amount is proportional to the ventilation volume, it is ideal to combine the humidifier installation with the ventilation system. For this application, the humidifier is installed on with the air supply side of the Lossnay.
(4) Conformation to Building Laws
The most important consideration here is humidification and dust removal; in these terms, it is recommended that a humidifier is added to the air conditioning system for the office system to allow adequate humidification. Installation of a filter on each air circulation system in the room is effective for dust removal, but if the outdoor air inlet is near the dust source, such as a road, a filter should also be installed on the ventilation system.
1.4 Effect
(1) Air conditioning and ventilation needs can be met on an individual basis.
(2) Operation is possible with a 24-hour system.
(3) Operation is simple with the switches being in the room. (A controller is not required.)
(4) Floor space is saved and thus the floor can be used to the maximum.
(5) Energy is conserved with the independent heat recovery.
(6) Fresh air air-conditioning is possible with the independent system.

2. Medium Size Office Building

2.1 System plan point
In recent building air conditioning systems, demands for a consistent rationalization from design through operation and control aspects are being made to meet diversified building needs. In the entire air conditioning facility, either the cooling/heating source equipment or specific air conditioning equipment is considered as being only one element. Thus, it is important to design this element so that it covers the user’s needs while providing total amenity. This air conditioning system plan is for a so-called company building that is largely divided into the general office section (hereinafter referred to as general floors) and special room sections including board rooms and conference rooms (hereinafter referred to as special floors). Furthermore, Building Management Laws are applied to the building due to the scale.
Setting outline
●
Building area : 862.2 m
2
●
Total floor area : 7,093 m
2
●
No. of floors : Basement, above ground 8, penthouse 1
●
Application per floor : Basement ....... Parking area
Ground floor ....... Large hall
1 to 5 ....... Offices
6 to 7 ....... Special rooms
Page 78
Heat
Load Total Shaft
Machine
Roof Total
source
room
Air conditioning
power (kW)
Required area (m
2
)
Air conditioning
system
Sleeve size
of beam
×
Q’ty
(Per floor)
Zoning
Refur-
bishing
Cleanliness
(Building
Management
Law)
Noise
Possible for each system (each air conditioner)
Possible for each outdoor air treatment unit (Per unit size)
Possible for each air conditioner
Possible for each outdoor air treatment unit (Per unit size)
Possible for each outdoor air treatment unit (Per unit size)
Same
as left
Same as left
Same as left
Same as left
Same as left
Possible by assembling required specification filter on air conditioner
Possible by assembling required specification filter on outdoor air treatment unit and fan coil unit
Possible by assembling required specification filter on air conditioner
Possible by assembling required specification filter on air conditioner and outdoor air treatment unit
Possible by assembling required specification filter on outdoor air treatment unit, air conditioner and fan coil unit
Noise control possible
Little noise emitted
Relatively loud
Little noise emitted, but louder than B system
Little noise emitted
ø100 × 162
ø100 × 162 ø250 × 108
ø100 × 45
ø250 × 189
ø100 × 144
ø250 × 21
Air-cooling heat pump chiller
+ Air handling unit on each floor
+ Floor-type fan coil unit (perimeter)
Air-cooling heat pump chiller
+ Ceiling embedded- type fan coil unit
+
Ceiling embedded­type outdoor air treatment unit
Air-cooling heat pump chiller Single suction method
Ceiling embedded- type air-cooling heat pump Package air conditioner (City Multi)
+
Ceiling embedded­type outdoor air treatment unit
B system + D system (combined use) (B system for general floors) (D system for special floors)
A
B
C
D
E
317 105 422 80 513 140 733
317 45 362 80 – 140 220
393 67 460 50 567 – 617
239 47 286 80 – 150 230
285 53 338 80 – 200 280
72
CHAPTER 6 ● Examples of Lossnay Applications
2.2 Current topics
For general office buildings of the past, centralized air conditioning methods allowing the total centralized control and systematization of the entire building (or divided into floor systems) were favoured due mainly to facility control, uniformity of operation hours, maintenance efficiency and building usage. However, when additional work was required to be done on these systems problems occurred.
A comparison of the following items in each system is shown in Table 1.
●
Energy conservation (air conditioning power)
●
Space saving (area required for air conditioning facilities)
●
Flexibility (zoning and refurbishing)
Table 1 Comparison of air conditioning systems
Page 79
: Air intake
: Supply diffuser FCU : Fan coil unit GU :
Outdoor-Air processing unit
2.4 Effect
(1) Individual control is possible
Individually dispersed air conditioning that creates a comfortable environment according to general floor and special floor needs is realised.
(2) Energy conservation
Wasted air conditioning energy is eliminated allowing great reduction in operation costs.
(3) Space saving
The Outdoor-Air Processing unit, fan coil unit and building air conditioner are all ceiling embedded-types, so the back of the ceiling is used effectively, saving machine room space and floor space.
(4) Construction saving
The ventilation functions have been unitised with the Outdoor­Air Processing unit, and all air conditioner units can be unitised allowing construction to be reduced.
(5) Simple architecture layout
Machine room space and main duct space for air conditioning are not required, so limits in the layout are reduced.
73
CHAPTER 6 ● Examples of Lossnay Applications
2.3 Proposed details
A) General floors
An independent dispersed-type control system incorporating an air cooling heat pump chiller and cassette-type fan coil unit for cooling and heating is used. This can cater for load fluctuations resulting from increases in office automation
systems or changes in partitions hence requiting independent control of each module zone (approx. 70 m
2
). Outdoor-Air Processing unit is used for ventilation and humidification, and construction and space is reduced by using a system ceiling and ceiling chamber method. (Table 1 B system)
B) Special floors
City Multi and Outdoor-Air Processing unit are applied as package-type independent units, located so as to conform with lighting fixtures, air outlets and suction inlets in rooms where the interior is important while ensuring the required air­conditioning quality. (Table 1 D system)
System using fan coil unit (general floors) General floor air conditioning facilities
New air conditioning Conversional air
system conditioning system
Heat source Air-cooling heat Air-cooling heat equipment pump chiller pump chiller
Air Outdoor air treatment Air handling unit Conditioner unit Outdoor-Air (1 unit on each floor)
Processing unit (8 units on each floor) ⇐ Floor-type fan coil
unit Ceiling embedded­type fan coil unit
Ratio with convertional air conditioning system as 100
Compaarison with conventional air conditioning system
Facility costs
Operation costs (including main-
tenance rate)
Air conditioning
power
Installation space (including roof-top installation space)
Chilling unit
<Sunny Pack>
Unit (mm)
Page 80
74
CHAPTER 6 ● Examples of Lossnay Applications
2.5 System trends
●
Creation of an environment including independence, management and control of each zone can be realised as work trends become more diversified.
●
Simultaneous cooling/heating system due to necessity from increased fixed sash windows and increase in office automation systems.
●
Attention is being paid to building management methods which manage not only air conditioning systems for several buildings at one location but also manage other information.

3. Multipurpose Tenant Building

3.1 System plan points
In many business district buildings, use of the lower floors for shops, halls and theatres, etc., and the middle and upper floors for offices and tenants is often seen. An air conditioning and ventilation system using a per floor method with each floor as a tenant unit is proposed in this example.
Setting outline
●
Application : Business (lower floors), office tenants (mid- to upper floors)
●
Building form : SRC (Slab Reinforced Concrete)
●
Total floor space : 6,334 m2(B1 to 8F)
●
Application per floor : B1: Storage, machine room
GF, 1F : Bank 2F, 3F : Theatre, concert hall 4F to 8F : Tenant offices
●
Air conditioning : Machine room installation-type package air conditioner, ceiling suspended cassette-type air
conditioner
●
Ventilation : Building Lossnay, ceiling suspended cassette-type Lossnay, straight centrifugal fan
3.2 Current topics
(1) The operation times of the lower floors and that in the mid- to
upper floors differ. (Efficiency and adaptability is required in control and operation aspects.)
(2) Maintainability is poor when the system is too dispersed.
(3) Handling of needs in tenant units is poor when the system is
too concentrated.
(4) When a centralized heat source system is applied, a
maximum load adaptability and maintenance control system is required.
(5) When ventilation is too dispersed, designing of the outer wall
becomes a problem.
Installation state
Total heat recovery unit
Filter unit
Pan-type humidifier
Package
Page 81
75
CHAPTER 6 ● Examples of Lossnay Applications
3.3 Plan details
(1) Lower floors for business
A machine room installation-type package and building Lossnay is applied as a centralized method for each unit. (One system for ground and 1st floor banking institution, one system for 2nd and 3rd floor hall.)
(2) Mid- to upper floors for office tenants
As an air conditioning system for each floor unit, a package air conditioner and Lossnay LP is combined in the machine room to handle the interior load and ventilation, and a ceiling suspended cassette-type package to handle the perimeter. The toilet and kitchenette are ventilated with a straight centrifugal fan on each floor, and supply for the outdoor air is provided to the LP Lossnay air supply. This allows independent operation and control for each floor.
(3) Control room, lounge, etc.
Independent use is possible with the ceiling suspended-type air-conditioner and ceiling suspended cassette-type Lossnay.
• 4F to 8F: Tenant offices – Lossnay installation sites:
machine room on each floor
To reduce installation space, a package-type LP Lossnay with built-in air-supply fan and filter is incorporated and combined with the air conditioner in the machine room on each floor.
1.600 × 650 × 500H
6.800
500 × 500
600 × 500
600 × 500
Lossnay
900 × 400
300 × 250
1.600 × 650 × 500H
Lossnay
OA shaft
500 × 400
Unit (mm)
Page 82
76
CHAPTER 6 ● Examples of Lossnay Applications
Air conditioning system diagram
3.4 Effect
(1) Management in tenant units is clear and simple.
(2) Maintenance is simple as the maximum centralization can be planned while having independent tenants.
(3) As ventilation units are considered per floor, there are few openings on the outer wall, making designing of the outer wall
more simple.
(4) Outdoor air cooling is possible while ventilating.
Unit (mm)
Page 83
4.3 Plan details
(1) Air conditioning
●
Space efficiency and comfort during cooling/heating is improved with ceiling embedded cassette-type package air conditioner.
(2) Ventilation
●
Room Entire area is ventilated by installing several ceiling embedded-type Lossnay units.
●
Salon corner Humidification is possible by adding a humidifier.
(Outdoor air is supplied to the toilet and kitchenette by setting the selection switch on the Lossnay unit for supply to the extra-high notch.)
●
Conference room Area is independently ventilated by installing a ceiling embedded-type or cassette-type Lossnay
●
Board room in each room.
●
Toilet, powder room
Area is exhausted with straight centrifugal fan or duct ventilation fan.
●
Kitchenette
(An adequate exhaust volume can be obtained by taking in outdoor air, with the toilet being ventilated constantly.)
●
Position of air intake/exhaust air outlets on outer wall The freshness of the outdoor air taken in by the Lossnay is important, thus considering
that the building is surrounded by
other buildings, the intake and exhaust ports must be separated as far as possible.
77
CHAPTER 6 ● Examples of Lossnay Applications

4. Urban Small-Scale Building

4.1 System plan points
This system is based on effectively using available space within a limited area by installing the air conditioner and ventilator in available excess space. For this application, the air flow must be considered for the entire floor with the ventilator installed in the ceiling space.
Setting outline
●
Application : Office
●
Building form : RC (Reinforced Concrete)
●
Total floor space : 552 m2(B1 to 5F)
●
Application per floor : B1: Parking area
GF to 5F: Office
●
Air conditioning : Package air conditioner
●
Ventilation : Ceiling embedded-type and cassette-type Lossnay, straight centrifugal fan, duct ventilation fan.
4.2 Current topics
(1) Three sides of the building are surrounded by other buildings,
and windows cannot be installed. (Dependency on mechanical ventilation is high.)
(2) Ample fresh outdoor air cannot be supplied. (Generally, only
Class 3 ventilation (forced exhaust) is possible.)
(3) If the exhaust in the room is large, odors from the toilet, etc.,
flow into the room.
(4) Humidification during winter is not possible.
}
}
}
GF layout 1F to 5F layout
PAC: Package air conditioner LS : Lossnay
Page 84
78
CHAPTER 6 ● Examples of Lossnay Applications
4.4 Effect
(1) Accurate ventilation is possible with Class 1 ventilation (forced simultaneous air intake/exhaust) using the Lossnay.
(2) Outdoor air supply to the toilet and kitchenette is possible with the Lossnay, and accurate ventilation is possible even in
highly sealed buildings.
(3) Flow of odors can be prevented with constant ventilation using an adequate ventilation volume.
(4) Humidification is possible by adding a simple humidifying unit to the Lossnay.

5. Hospitals

5.1 System plan points
The principle of ventilation in hospitals requires adequate exhausting from the generation site and ensuring a supply of ample fresh air. An appropriate system would be an independent ventilation system with Class 1 ventilation (forced simultaneous air intake/exhaust). The fan coil and package air conditioning are used according to material and place, and the air conditioned room is ventilated with the ceiling embedded-type Lossnay. The toilet and kitchenette, etc., are ventilated with a straight centrifugal fan.
Setting outline
●
Building form : RC (Reinforced Concrete)
●
Total floor space : 931 m2(GF to 2F)
●
Application per floor : GF : Waiting room, diagnosis rooms, surgery theatre, director room, kitchen
1F : Patient rooms, nurse station, rehabilitation room, cafeteria 2F : Patient rooms, nurse station, head nurse room, office
●
Air conditioning : Fan coil unit, package air conditioner
●
Ventilation : Ceiling embedded-type Lossnay, straight centrifugal fan
5.2 Current topics
(1) Prevention of in-hospital transmission of diseases
(Measures meeting needs for operating rooms, diagnosis rooms, waiting rooms and patient rooms are required.)
(2) Adequate ventilation for places where odors are generated
(Measures to prevent odors from toilets from flowing to other rooms are required.)
(3) Shielding of external noise
(Shielding of noise from outside of building and noise from adjacent rooms and hallway is required.)
(4) Assurance of adequate humidity
(5) Energy conservation
Page 85
Reception
79
CHAPTER 6 ● Examples of Lossnay Applications
5.3 Plan proposals
(1) Air conditioning
● Centralized heat source control using a fan coil for the
general system allows efficient operating time control and energy conservation.
● 24-hour system using a package air conditioner for special
rooms (surgery theatre, nurse station, special patient rooms, waiting room) is the most practical.
(2) Ventilation
●
Hall system
Independent system using centralized control with LP Lossnay or independent system with installation of ceiling suspended-type Lossnay
●
Surgery theatre
Combination use of LP Lossnay and package air­conditioner 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 possible for required rooms.
●
Positive/negative pressure adjustment, etc., is possible by setting main unit selection switch to extra-high notch (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 is supplied from the hallway ceiling with the straight centrifugal fan, and is distributed near the air conditioner after the air flow is reduced.
●
Kitchen
Exhaust with negative pressure ventilation fan or straight centrifugal fan. Outdoor air is supplied with the straight centrifugal fan.
●
Machine room
Exhaust with positive pressure ventilation fan.
GF layout
1F layout
2F layout
Medicine supply storage
Gastro camera room
X-ray room
Kitchen
Surgery
theatre
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
Nurse beds
Nurse
station
Head nurse room
Office
Treatment room
Page 86
80
CHAPTER 6 ● Examples of Lossnay Applications
5.4 Effect
(1) The following is possible by independently ventilating the air-conditioned rooms with the Lossnay:
●
Transmission of diseases can be prevented by shielding the air between rooms.
●
Infiltration of outside noise can be prevented with the Lossnay Core’s soundproof properties.
●
As outdoor air does not need to be taken in from the hallway, the door can be sealed, shutting out hallway noise.
●
Humidification is possible by adding a humidifier.
(2) By exhausting the toilet, etc., and supplying outdoor air to the hallway:
●
Flowing of odors to other rooms can be prevented.

6. Schools

6.1 System plan points
A comfortable environment in classrooms is necessary to improve the children and students’ desire to study. Schools near airports, railroads and highways have sealed structures to soundproof the building, and thus air conditioning and ventilation facilities are required. This is also true for schools in polluted areas such as industrial districts. At university facilities which have a centralized design to efficiently use land and to improve the building functions, the room environment must also be maintained with air conditioning.
6.2 Current system details and problem points
(1) Mainly single duct methods, fan coil unit methods, or package methods are used for cooling/heating, but the diffusion rate
is still low, and water-based heaters are still the main source of heating.
(2) The single duct method is difficult to control according to the usage state, and there are problems in running costs.
(3) Rooms are often ventilated by opening the windows or using a ventilation gallery, where although this provides ample
ventilation volume it may create a problem of infiltration of outside noise.
6.3 Building outline
Total floor space : 23,000 m
2
Building outline : Prep school (high school wing)
Memorial hall wing Library wing Main management wing
Page 87
81
CHAPTER 6 ● Examples of Lossnay Applications
6.4 Plan details
(1) To pursue comfort, save energy and space, an air
conditioning and ventilation system using a ceiling embedded-type fan coil unit and ceiling embedded-type Lossnay was applied.
(2) Automatic operation using a weekly program timer was
applied, energising when the general classrooms and special classrooms are to be used.
(3) By using a ventilation system with a total heat recovery unit,
energy is saved and soundproofing is realised.
6.5 Conditions for air-conditioning in schools
(1) Zoning according to application must be possible.
(2) Response to load fluctuations must be swift.
(3) Ventilation properties must be good.
(4) The system must be safe and rigid.
(5) Expansion of the facility must be easy.
(6) Installation on existing buildings must be possible.
(7) Installation and maintenance cost must be low.
6.6 System trends
(1) It is believed that environmental needs at schools will continue to progress towards high quality, and various factors such
as temperature/humidity, noise, natural lighting, and colour must be considered at the design stages. Important topics are air conditioning, ventilation and soundproofing.
(2) Independent heating using a centralized control method is mainly applied when the air conditioner is for heating only. For
cooling/heating, a combination of a fan coil method and package-type is the main method used.
(3) Highly accurate Class 1 ventilation is applied for the ventilation method, and the total heat recovery unit is 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)
Page 88
82
CHAPTER 6 ● Examples of Lossnay Applications

7. Hotels (convention halls, wedding halls)

7.1 System plan points
Hotels in Japan often have functions such as a resort hotel at tourist spots, convention hotel with conference and banquet halls, and business hotels for short-term stays. These are all labeled as hotels, and often, more importance is laid on the wedding, convention and banquet halls, etc. This is because air conditioning systems in these places must have a ventilation treatment system that can handle extremely large fluctuations in loads, tobacco smoke and removal of odors.
7.2 Current systems and problem points
CO and CO2 permissible values, removal of odors, and tobacco smoke are often considered as standards for ventilation and often the ventilation is set at 30 m
3
/h·person to 35 m3/h·person. Several outdoor air introduction-type package air conditioners or air handling unit facilities are often used, but, these are greatly affected by differences in capacity, ratio of smokers and length of stay.
7.3 Plan details
This proposed plan has two examples with the use of a Lossnay as a ventilator for total heat recovery in the air conditioned conference room, and the use of several outdoor air type package air-conditioners for convention and banquet halls.
A) Conference room
Heat recovery ventilation is executed with constant use of the Lossnay unit, but when the number of persons increases suddenly and the CO
2
concentration reaches a set level (for example, 1,000 ppm in the Building Management Law), a separate centrifugal fan operates automatically. This system can also be operated manually to rapidly remove smoke and odors.
B) Convention and banquet halls
Basically, this system is composed of several outdoor air introduction-type package air conditioners and straight centrifugal fans for ventilation. However, an inverter controller is connected to the centrifugal fan so that it is constantly at 50 percent of the operation state, allowing fluctuations in ventilation loads to be handled. By interlocking with several package air-conditioners, detailed handling of following up the air condition loads in addition to the ventilation volume is possible. Systems using Lossnay are also possible.
Conference room ventilation system diagram
Convention and banquet hall ventilation system diagram
LS : Lossnay EX : Centritugal fan PAC: Package air conditioner
EX : Centritugal fan PAC: Package air conditioner IB : Inverter controller
Page 89
83
CHAPTER 6 ● Examples of Lossnay Applications
7.4 System trends
The load characteristics at hotels is complex compared to general buildings, and are greatly affected by the bearing, time, and operation state as mentioned above. Further to this, the high ceilings in meeting rooms and banquet halls, requires preheating and precooling to be considered. Further research on management and control systems and product development will be required in the future to pursue even further comfortable control within these spaces.
8.

Public Halls (combination facilities such as day-care centres)

8.1 System plan points
Air conditioning and ventilation facilities for buildings located near airports and military bases, etc., that require soundproofing, have conventionally been of the centralized method. However, independent dispersed air conditioning and ventilation has been demanded due to the need for operation in zones, as well as for energy conservation purposes. This system is a plan for these types of buildings.
Setting outline
●
Building form : Above ground 2, Total floor space: 385 m
2
●
Application : GF Study rooms (2 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
8.2 Conventional system and topics
(1) Conventional systems have used centralized methods with air handling units, and air conditioning and ventilation were
generally performed together.
(2) Topics
1) Special knowledge is required for operation, and there are problems in response to the users’ needs.
2) When the centralised method is used, the air even in rooms that are not being used is conditioned, increasing running costs unnecessarily.
3) Machine room space is necessary.
4) Duct space is necessary.
8.3 Plan 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 is used in each room, and a silence chamber, silence-type supply/return grille, silence duct, etc. is incorporated on the outer wall to increase the total soundproofing effect.
Page 90
Soundproofing standards Soundproofing effect
High pressure level difference Study room : 34.0 dB
30 dB or more Rest room : 47.2 dB
84
CHAPTER 6 ● Examples of Lossnay Applications
8.4 Effect
(1) Operation is possible without special knowledge, so management is easy.
(2) Operation is possible according to each room’s needs, and is thus energy-saving.
(3) Soundproof ventilation is possible with the separately installed ventilators.
(4) Energy saving ventilation is possible with the heat recovery ventilation.
(5) Space saving with the ceiling embedded-type.
➞
GF 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
Page 91

CHAPTER 7
Installation Considerations

Page 92
CHAPTER 7 ● Installation Considerations
1. LGH-Series Lossnay Ceiling Embedded-Type (LGH-RX
4 Series)
LGH-15 · 25 · 35 · 50 · 65 · 80 · 100RX
4 models
■ Installation diagram
A
EA
(Exhaust air)
OA
(Outside air)
Duct downward slope 1/30 or more (to wall side)
(Rainwater entrance prevention) Deep-type hood or
weather cover
EA (Exhaust air)
OA (Outside air)
150 to 250
600 or more
Duct diameter ø200 (ordered by customer)
Suspension bolt position (ordered by customer)
Suspension bolt position
Inspection
opening
Inspection opening
Exhaust air grill
B
Lossnay Core/ air filter/ fan maintenance space
(Return air)
Suspension bolt position
414
Suspension bolt position
Supply air grill
414
Supply/ exhaust air grill
RA
SA (Supply air)
Unit (mm)
●
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 frosting.
●
It is possible to change the direction of the outside air ducts (OA and EA side).
●
It is possible to attach a suspension bolt.
●
Do not install the vent cap or round hood where it will come into direct contact with rain water.
Air volume (m3/h) Model
Dimension
AB
150 LGH-15RX
250 LGH-25RX
350 LGH-35RX
500 LGH-50RX
650 LGH-65RX
800 LGH-80RX
1000 LGH-100RX
4 700 641
4 700 765
4 790 906
4 790 1,048
4
4 1,030 1,036
4 1,030 1,263
810 985
LGH-150 · 200RX
4
■ Installation diagram
Ceiling Exhaust grille (user supplied)
EA
(exhaust-air outlet)
Air-supply grille (user supplied)
OA
(fresh-air intake)
Duct (user supplied)
Duct (user supplied)
Duct incline Over 1/30 (toward the wall)
to prevent entry of rainwater
EA
(exhaust-air outlet)
OA
(fresh-air intake)
suspension
bolt position
B
Ceiling suspension bolt
(user supplied)
(user
supplied)
450( 600) Inspection port
Duct diameter 250 (user supplied)
A
450( 600)
Inspection port
Heat exchanger/filter maintenance space
Exhaust grille (user supplied)
Y piping,Dwindle pipe
(user supplied)
Min. 600
150~250
Ceiling suspension bolt position
RA
(return air)
Exhaust grille
(return air)
RA
Air-supply grille (user supplied)
Air-supply grille
(user supplied)
Air-supply grille
SA
(supply air)
SA
(supply air)
Unit (mm)
Ceiling suspension
bolt position
Duct diameter 200
(user supplied)
●
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 frosting.
●
If necessary, order a weather cover to prevent rain water from direct contact or entering the unit.
Air volume (m3/h) Model
Dimension
AB
4 1,030 1,046
4 1,030 1,273
●
Ducting
1500 LGH-150RX
2000 LGH-200RX
Indoor Outdoor
Heating-insulation material
Taping
Duct
Duct connecting flange
Should secure with airtight tape to prevent air leakage.
Heating-insulation material
Taping
Should secure with airtight tape to prevent air leakage. Cover duct with insulation foam prevent condensation.
86
Page 93
87
CHAPTER 7 ● Installation Considerations
(1) The ceiling embedded-type: 150 · 250 · 350 · 500 · 650 · 800 · 1000 · 1500 and 2000 m3/h types are available.
Select an adequate model according to the room size, air volume for the application and noise levels.
(2) The LGH-RX
4 types have an extra-high notch. This setting is for when a long duct is used or when a large air volume is
required. The positive and negative pressures of the room can also be adjusted with this.
LGH-15 · 25 · 35 · 50 · 65 · 80 · 100RX
4
LGH-150 · 200RX4
High and Extra High switch
SW3
Exhaust air
SE4
Supply air
High
E-High
High
E-High
High and Extra High switch
High
E-High
High
E-High
SW3
Exhaust air
SE4
Supply air
Multi-ventilation mode setting (Refer to Technical Manual (controls) page 70)
RX
4
type is available to make 9 fan speed setting patterns of SA and EA fans for High notch.
RX
3 type have only 4 fan speed patterns for High.
Setting on PCB dip switch table.
*Factory setting
Power supply / exhaust mode
Power supply mode (Fixed Exhaust fan at Low mode)
Power Exhaust mode (Fixed Supply fan at Low mode)
Energy saving ventilation mode Fixed Both of fans at Low Mode
Switch for High and E-High Remote Controller
Model comparison
Dip switch
Switch for High and E-High
High Low
RX
4 RX3
SW2-4 SW2-5 SW4 SW3 SA EA SA EA
Off Off E-High E-High E-High E-High Low Low
««
Off Off High High High High Low Low ««
*
Off Off High E-High High E-High Low Low ««
Off Off E-High High E-High High Low Low ««
Off On E-High E-High Low Low Low « × Off On High High Low Low Low « × On Off E-High Low E-High Low Low « × On Off High Low High Low Low « ×
On On Low Low Low Low «
Not
Available
Not
Available
Not
Available
Not
Available
Not
Available
Not
Available
(SW2-
4Off, SW2-5On)
➞ ➞ ➞ ➞ ➞ ➞ ➞ ➞ ➞
Page 94
88
CHAPTER 7 ● Installation Considerations
1.1 Selecting Duct Attachment Direction
You can choose between two directions for the outside duct (OA, EA) piping direction, to improve construction.
Standard Construction Construction with the Direction Changed
OA
EA
OA
EA
OA
EA
*A space is
necessary to prevent rain water from entering.
■ It is possible
to set the unit close to a wall.
■ You can avoid
obstructions of the supply and exhaust ducts by lights or air conditioners.
Light, etc.
1.2 Installation and maintenance
(1) Always leave an inspection hole ( 450) on the filter and Lossnay Core removal side.
(2) Always insulate the two ducts outside the room (intake air and exhaust air ducts) to prevent frosting.
(3) Enforce measures to prevent rain water from entering.
●
Apply a slope of 1/30 or more towards the wall to the two ducts outside the room (intake air and exhaust air ducts).
●
Do not install the vent cap or round hood where it will come into direct contact with rain water.
(4) Use the optional parts “control switch” (Ex. PZ-41SLB, etc.) for the RX
4-type.
A centralized controller can also be used.
1.3 Installation applications
(1) Combined installation of two units
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 turned over, and installed as shown below. (This is applicable when installing two units in one classroom, etc.)
(2) System operation with air conditioner
Air conditioning systems with independent dispersed multiple unit air-conditioners are increasing due to merits such as improved controllability, energy conservation and space saving. For these types of air conditioning systems, combined operation of the dispersed air conditioners with the Lossnay, is possible.
EA
SA SA
RA RA
OA EA
Reversed installation
Lossnay Lossnay
Inspection
opening
Standard installation
Cassette-type packaged air conditioner or fan coil unit
Return grill
Exhaust Air intake
Air intake
Ceiling embedded­type Lossnay
Ceiling embedded-type package air conditioner or fan coil unit
Return grill
Ceiling
Ceiling
Exhaust
Ceiling embedded­type Lossnay
Page 95
89
CHAPTER 7 ● Installation Considerations

2. Building Lossnay Unit Horizontal-type (LU-500)

2.1
Main unit installation surface diagram (anchor bolt installation position)
2.2 Maintenance space
Unit (mm)
Unit (mm)
200 × 3 ＝ 600
2050
8 pieces
× 12 × 18 slots
Pitch
Min. 800 is required for air filter core removal space. Removal from opposite side is also possible.
2.3 Dimensions and flange dimensions
LU-500
Air filter Lossnay Core removal direction. A space of at least 800 mm is required. The Lossnay Core can also be removed from the opposite side.
130
130
3.5
860
3.5
Interconnection seal
10
860
480
340
200
300
130
80
60
850 890
1000
850 890
1000
2100
50
100
25
200
50
100
80
25
Chamber mounting screws (M8 screws)
12 × 8 slot
3.5130
130
3.5
Air filter System components can be attached (4 locations).
Air filter Lossnay Core removal cover
Lossnay Cores are divided into 4 units.
pitch 200 × 3 = 600
pitch 200 × 3 = 60
160
pitch 200 × 4 = 800
80
Unit (mm)
Page 96
90
CHAPTER 7 ● Installation Considerations
2.4 Transportation and installation
The product is shipped in the fully assembled state. Transport the unit gently and do not apply shock or tilt the unit.
(1) Use eyebolts (or eyenuts) and rope when lifting the unit. Make sure that the rope can withstand the weight of the unit.
Always use all four eyebolts, and fix the rope. Adjust the rope length so that the angle between the rope and the unit is 45° or more.
(2) Use filler plates to protect the panel so that the panel is not damaged by the rope during lifting. (3) The unit will be damaged if the rope directly contacts the unit. (4) The foundation must be made of concrete. The concrete foundation must be level and have ample strength. (5) Install the unit perpendicularly to the foundation and securely fix the unit with anchor bolts. (6) Install the unit where rain water will not come into contact, and where rain water will not infiltrate the unit from the ducts.
Caution
This unit has indoor specifications and cannot be installed in sites where it will come into contact with rain water or in high temperature, high humidity locations.
45¡
45¡
45¡
or more
45¡
or more
Rope
Reinforcement material
Eye bolt Eye nut
Horizontal flange
Main unit
LU-502 · 503 · 504 · 505 Unit (mm)
ABCD E
LU-502 1730 1170 1250 1210 Pitch 100 × 10 = 1000 LU-503 2600 2040 2120 2080 Pitch 100 × 20 = 2000 LU-504 3470 2910 2990 2950 Pitch 100 × 27 = 2700 LU-505 4340 3780 3860 3820 Pitch 100 × 36 = 3600
860
960
50 50
890
Pitch 100 × 8 = 800
930
D
C
E
850
2100
200
100 850
100
480
A
80 B
80
480
B
Unit (mm)
ø10 hole
Flange details
Lossnay core
Air filter can be installed (optional)
Core, air filter removal cover
Duct connection flange
Page 97

CHAPTER 8
Filtering for Freshness

Page 98
92
CHAPTER 8 ● Filtering for Freshness

1. Necessity of Filters

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

2. Data Regarding Dust

The particle diameter of dust and applicable range of filters are shown in Table 1, and representative data regarding outdoor air dust concentrations and indoor dust concentrations is shown in Table 2.
Table 1 Aerosol particle diameters and applicable ranges of various filters
Aerosol particle diameter (µ m)
Solid particles
Fumes Dust
Mist
Clay
Oil fumes
Tobacco smoke
Carbon black
ZnO fumes
Sea salt particles
Atmospheric
dust
Fine dust, coarse dust fillers
Cement
Pollen
Viruses
Bacteria
Hair
Medium to high efficiency filters
HEPA filter
Coal dust
Fry ashes
Mud Sand
Sprays
Fluid particles
Air filters
Major particles
Aerosol particle
0.001 0.01 0.1 0.3 1 10 100 1000
Table 2 Major dust concentrations
Type Reference data
Outdoor air floating 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 (product vending stores) 5 mg/h per person
Applications with no tobacco smoke 5 mg/h per person
Remarks:
1. The core diameter of outdoor air dust is said to be 2.1 µ m, and the 11 types of dust (average diameter 2.0 µ m) as set by JIS Z 8901 as performance test particles are employed.
2. Dust in office rooms is largely caused by smoking, and the core diameter is 0.72 µ m. The 14 types of dust (average 0.8 µm) as set by JIS Z 8901 as performance test particles are employed.
3. The core diameter of dust generated in rooms where there is no smoking is approximately the same as outdoor air.
4. Smoking in general offices (as per Japan): Percentage of smokers : Approx. 70% (adult men) Average number of cigarettes : Approx. 1/person·h (including non-smokers) Smoking length of cigarette : Approx. 4 cm Amount of dust generated by one cigarette : Approx. 10 mg/cigarette
Page 99
93
CHAPTER 8 ● Filtering for Freshness
Tested
dust
Measurement
method
Filter type
Applicable
model
Commercial Lossnay (LGH)
Optional Part for model LGH-15RX
4 -
200RX4
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

Model PZ-15RFM PZ-25RFM PZ-35RFM PZ-50RFM PZ-65RFM PZ-80RFM PZ-100RFM
Dimension (mm)
A 554 330 395 466 429 448 561
B 121 147 174 174 209 236 236
Number of filters perset 1222222
Note: This is one set per main body.
PZ-15RFM
3.1 High-Efficiency Filter (Optional Parts)
A
B
25
AIR
FLOW
100
50 100 150 200 250
50
0
Air volume (m
3
/h)
Pressure Loss (Pa)
PZ-25RFM
100
100 200 300 400
50
0
Air volume (m
3
/h)
Pressure Loss (Pa)
PZ-35RFM
100
100 200 300 400 500
50
0
Air volume (m
3
/h)
Pressure Loss (Pa)
PZ-65RFM
200 400 600 800
100
50
0
Air volume (m
3
/h)
Pressure Loss (Pa)
PZ-50RFM
100
200 400 600
50
0
Air volume (m
3
/h)
Pressure Loss (Pa)
PZ-80RFM
100
200 400 600 800 1000
50
0
Air volume (m
3
/h)
Pressure Loss (Pa)
PZ-100RFM
200 400 600 800 1000 1200
Air volume (m
3
/h)
100
50
0
Pressure Loss (Pa)
3.2 Pressure Loss
■ Pressure Loss Characteristics
Page 100
94
CHAPTER 8 ● Filtering for Freshness
The ability of the filters used within 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 (µ m)
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