CA1078820A - Heat and moisture transferring system - Google Patents
Heat and moisture transferring systemInfo
- Publication number
- CA1078820A CA1078820A CA282,233A CA282233A CA1078820A CA 1078820 A CA1078820 A CA 1078820A CA 282233 A CA282233 A CA 282233A CA 1078820 A CA1078820 A CA 1078820A
- Authority
- CA
- Canada
- Prior art keywords
- heat
- air
- moisture
- set forth
- exchanging
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired
Links
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- 239000004020 conductor Substances 0.000 claims abstract description 5
- 239000007788 liquid Substances 0.000 claims description 15
- 230000005484 gravity Effects 0.000 claims description 10
- 239000011159 matrix material Substances 0.000 abstract description 25
- 230000015572 biosynthetic process Effects 0.000 abstract description 21
- 238000011084 recovery Methods 0.000 description 16
- 239000003507 refrigerant Substances 0.000 description 15
- 238000010438 heat treatment Methods 0.000 description 11
- 239000012298 atmosphere Substances 0.000 description 10
- 230000001965 increasing effect Effects 0.000 description 10
- 230000000694 effects Effects 0.000 description 9
- VOPWNXZWBYDODV-UHFFFAOYSA-N Chlorodifluoromethane Chemical compound FC(F)Cl VOPWNXZWBYDODV-UHFFFAOYSA-N 0.000 description 7
- 238000010276 construction Methods 0.000 description 6
- 239000006096 absorbing agent Substances 0.000 description 5
- 238000005192 partition Methods 0.000 description 5
- 230000003068 static effect Effects 0.000 description 5
- 239000010425 asbestos Substances 0.000 description 4
- 238000001704 evaporation Methods 0.000 description 4
- 238000002474 experimental method Methods 0.000 description 4
- 229910052895 riebeckite Inorganic materials 0.000 description 4
- 238000001816 cooling Methods 0.000 description 3
- 238000007710 freezing Methods 0.000 description 3
- 230000008014 freezing Effects 0.000 description 3
- 238000009423 ventilation Methods 0.000 description 3
- 230000002159 abnormal effect Effects 0.000 description 2
- PXBRQCKWGAHEHS-UHFFFAOYSA-N dichlorodifluoromethane Chemical compound FC(F)(Cl)Cl PXBRQCKWGAHEHS-UHFFFAOYSA-N 0.000 description 2
- 235000019404 dichlorodifluoromethane Nutrition 0.000 description 2
- KWGKDLIKAYFUFQ-UHFFFAOYSA-M lithium chloride Chemical compound [Li+].[Cl-] KWGKDLIKAYFUFQ-UHFFFAOYSA-M 0.000 description 2
- 239000000463 material Substances 0.000 description 2
- 238000004804 winding Methods 0.000 description 2
- UXVMQQNJUSDDNG-UHFFFAOYSA-L Calcium chloride Chemical compound [Cl-].[Cl-].[Ca+2] UXVMQQNJUSDDNG-UHFFFAOYSA-L 0.000 description 1
- 239000004338 Dichlorodifluoromethane Substances 0.000 description 1
- 206010037660 Pyrexia Diseases 0.000 description 1
- HODFCFXCOMKRCG-UHFFFAOYSA-N bitolterol mesylate Chemical compound CS([O-])(=O)=O.C1=CC(C)=CC=C1C(=O)OC1=CC=C(C(O)C[NH2+]C(C)(C)C)C=C1OC(=O)C1=CC=C(C)C=C1 HODFCFXCOMKRCG-UHFFFAOYSA-N 0.000 description 1
- 229910001628 calcium chloride Inorganic materials 0.000 description 1
- 239000001110 calcium chloride Substances 0.000 description 1
- 239000003795 chemical substances by application Substances 0.000 description 1
- 229940000425 combination drug Drugs 0.000 description 1
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- 239000011148 porous material Substances 0.000 description 1
- 235000002020 sage Nutrition 0.000 description 1
- 238000010792 warming Methods 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F3/00—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems
- F24F3/12—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling
- F24F3/14—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling by humidification; by dehumidification
- F24F3/1411—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling by humidification; by dehumidification by absorbing or adsorbing water, e.g. using an hygroscopic desiccant
- F24F3/1423—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling by humidification; by dehumidification by absorbing or adsorbing water, e.g. using an hygroscopic desiccant with a moving bed of solid desiccants, e.g. a rotary wheel supporting solid desiccants
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F12/00—Use of energy recovery systems in air conditioning, ventilation or screening
- F24F12/001—Use of energy recovery systems in air conditioning, ventilation or screening with heat-exchange between supplied and exhausted air
- F24F12/002—Use of energy recovery systems in air conditioning, ventilation or screening with heat-exchange between supplied and exhausted air using an intermediate heat-transfer fluid
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F3/00—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems
- F24F3/12—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling
- F24F3/14—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling by humidification; by dehumidification
- F24F2003/1458—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling by humidification; by dehumidification using regenerators
- F24F2003/1464—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling by humidification; by dehumidification using regenerators using rotating regenerators
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F12/00—Use of energy recovery systems in air conditioning, ventilation or screening
- F24F12/001—Use of energy recovery systems in air conditioning, ventilation or screening with heat-exchange between supplied and exhausted air
- F24F2012/007—Use of energy recovery systems in air conditioning, ventilation or screening with heat-exchange between supplied and exhausted air using a by-pass for bypassing the heat-exchanger
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F2203/00—Devices or apparatus used for air treatment
- F24F2203/10—Rotary wheel
- F24F2203/1004—Bearings or driving means
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F2203/00—Devices or apparatus used for air treatment
- F24F2203/10—Rotary wheel
- F24F2203/1012—Details of the casing or cover
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F2203/00—Devices or apparatus used for air treatment
- F24F2203/10—Rotary wheel
- F24F2203/1016—Rotary wheel combined with another type of cooling principle, e.g. compression cycle
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F2203/00—Devices or apparatus used for air treatment
- F24F2203/10—Rotary wheel
- F24F2203/1032—Desiccant wheel
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F2203/00—Devices or apparatus used for air treatment
- F24F2203/10—Rotary wheel
- F24F2203/104—Heat exchanger wheel
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F2203/00—Devices or apparatus used for air treatment
- F24F2203/10—Rotary wheel
- F24F2203/1056—Rotary wheel comprising a reheater
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F2203/00—Devices or apparatus used for air treatment
- F24F2203/10—Rotary wheel
- F24F2203/1068—Rotary wheel comprising one rotor
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F2203/00—Devices or apparatus used for air treatment
- F24F2203/10—Rotary wheel
- F24F2203/1084—Rotary wheel comprising two flow rotor segments
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
- Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
- Y02B30/56—Heat recovery units
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Central Air Conditioning (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Abstract
HEAT AND MOISTURE TRANSFERRING SYSTEM
ABSTRACT OF THE DISCLOSURE
A system for effecting heat and moisture exchange between out door air and return air passing through an air supply passage and an air exhaust passage communicated with a heated space. The system including heat and moisture transferring device mounted in airtight fashion and located across the air supply passage and the air exhaust passage and a heat transmitting system having a closed circuit for circulating a heat transmitting medium and including two heat exchangers each mounted in one of the two air passages upstream of the heat and moisture transferring device. The heat and moisture transferring device includes heat and moisture trans-ferrer matrix made of a moisture absorptive and heat conductive material for effecting transfer of heat and moisture between return air and outdoor air. The heat transmitting system precools and preheats the return air and the outdoor air respectively by effecting heat exchange between the return air and the outdoor air through the agency of the heat transmitting medium so as to thereby prevent the formation of dew and frost on the surfaces of the transferring matrix of the heat and moisture transferring device.
ABSTRACT OF THE DISCLOSURE
A system for effecting heat and moisture exchange between out door air and return air passing through an air supply passage and an air exhaust passage communicated with a heated space. The system including heat and moisture transferring device mounted in airtight fashion and located across the air supply passage and the air exhaust passage and a heat transmitting system having a closed circuit for circulating a heat transmitting medium and including two heat exchangers each mounted in one of the two air passages upstream of the heat and moisture transferring device. The heat and moisture transferring device includes heat and moisture trans-ferrer matrix made of a moisture absorptive and heat conductive material for effecting transfer of heat and moisture between return air and outdoor air. The heat transmitting system precools and preheats the return air and the outdoor air respectively by effecting heat exchange between the return air and the outdoor air through the agency of the heat transmitting medium so as to thereby prevent the formation of dew and frost on the surfaces of the transferring matrix of the heat and moisture transferring device.
Description
~C~78~
Thls invention relates to a heat and moisture transferring system for effecting exchange of heat and moisture between two streams of air.
There have hitherto been known in the art two types of heat and moisture transferring devices, or devices of the rotary type and the static type, operat~ve to simultaneously effect heat exchange with respect to latent heat and sensible heat, thereby enabling heat to be recovered with a high degree of efficiency.
In one aspect of the present invention there is :~
provided a system for transferring heat and moisture between first and second air streams comprising, in combination: a first conduit means for said first air stream; a second conduit means for said second air stream; heat and moisture transferring means comprlsing a multitude of open-ended air passages defined by moisture absorptive and heat conductive material, a first set of :
said air passages being disposed in said first conduit -means for permitting said first air stream to pass .
thèrethrough and a second set of said air passages ;
being disposed in said second conduit means for permitting said second air stream to pass therethrough; means . :
- disposing the first and second set o air passages alternatively so that heat and moisture are transferred ..
between the first and second air streams passing through .
2S said passages through the moisture absorptive and heat conductive material; and a heat transmitting system including a first heat exchanging means disposed in said .~.
first condui.t means upstream of said heat and moisture transferring means for exchanging heat between said first air stream and a heat transmitting medium, a second heat exchanging means disposed in said second conduit means upstream of saia heat and molsture transferring means for exchanging heat ~etween sa;d second air stream and said heat transmltting medïum, and thîrd conduit means connecting said first and second heat exchanging means together for forming a closed circuit for said heat transmitting medium.
In the drawings illustrating the invention:
Fig. 1 is a perspective view, with certain parts being broken away, of a rotary type heat and mois-ture transferring device used in the heat and moisture transferri~g system according to the present invention;
Fig. 2 is a perspective view schematically showing essential portions of a static type heat and moisture transferring device used in the heat and moisture transferring system according to the invention;
Fig. 3 is a schematic view of a heat and moisture transferring system of the prior art;
Figs. 4 and 5 are psychrometric charts showing the relation between the temperature and the humidity of the air passing through the system shown in Fig. 3;
Fig. 6 is a schematic view of the heat and moisture transferring system comprising one embodiment of the invention;
Fig. 7 is a schematic view of another embodi-ment of the invention;
Fig. 8 is a psychrometric chart showing the I temperature-humidity characteristics of the embodiment shown in Fig. 6;
Fig. 9 is a graph showing the relation between the preheating ratio and the total heat recovery efficiency;
l 1 - l a-: ~ .
t7~2~
~ig. 10 ls a schematic view of still another embodiment of the invention;
Fig. 11 is a schematic view of a further embodiment of the invention; and Fig. 12 is a perspective view, with certain parts being broken away, of the embodiment shown in Fig. 6.
Fig. 1 shows a commonly used device of the rotary type. As shown, the heat and moisture transferring device 3 comprises a heat and moisture transferrer matrix 4 formed by winding, in roll rorm, a sheet of asbestos paper consisting of plane member and a corrugated member both impregnated with a moisture absorbing agent. As shown in :.
Fig. 3, the device 3 is mounted for rotation of the heat and moisture transferrer matrix 4 across an air supply pas- ~
sage 1 and an air exhaust passage 2 divided by a partition `.
wall 11 lnto upper and lower passages or left and right passages. One example of the rotary type heat and moisture transferring device is disclosed in US Patent `
No. 3,587,723. ~leanwhile Fig. 2 shows a commonly used heat and moisture transferring device of the static type comprising a plurality of corrugated members 4a of ~: ~
asbestos paper impregnated with a moisture absorbing ~ .
agent and a plurality of plane members 4b of the same material as the corrugated members 4a impregnated with :~
the same moisture absorbing agent, such corrugated members 4a and plane members 4b being mounted across the two air passages ln such a manner that they are -lb-~'7~ 20 l alternately piled in vertically stacked relationshlp so that the layers of the corrugated members 4a will intersect one another perpendicularly and the layers of the corrugated members 4a of odd numbers communicate with the air supply passage l while the layers of the corrugated members 4a of even numbers communicate with the air exhaust passage, for example. This type of device ~s disclosed in US Patent No. 3,666,oo7.
Assume that, when heating of a space is effected 10 in wintertime, such heat and moisture transferring device ~.
3 is used for recovering heat from return air RA from the heated space and exhausting the return air RA as exhaust air EA to the atmosphere, while the recovered heat is given to outdoor air OA which is introduced into the space as supply air SA. If the return air RA
has an inordinately high moisture content, or if, as shown in a psychrometric chart i.n Fig. 4, the outdoor air OA has a temperature 0C and a humidity 75% and the return air RA from the heated space has a temperature ~ :
20C and a humidity 95%, for example, the.straight line connecting the two points representing the outdoor air and return air in the chart will intersect the saturation line of relative humidity 100% at a point A
(17C) and a point B (5C). When this is the case, the return air RA will move downwardly along the broken line as it is being cooled by the heat and moisture transferring device 3 until its humidity becomes lQ0%
at the polnt A where it moves outwardly of the saturation line. The broken line will intersect the saturation line again at the point B. The return air is exhausted to ~.~q~38~
1 the atmosphere as exhaust air EA. When this phenomenon occurs, dew wlll be formed on the surfaces of the heat and moisture transferrer matrix 4 between the points A
and B, because the humidity o~ the return air RA is over 100% in this section of the broken line and the moisture in the return air RA condenses. The formation of dew on the sur~aces of the heat and moisture trans- ;:
.ferrer matrix 4 will cause effluence of the moisture absorbing agent, thereby causing a reduction in the ~ :
10 moisture absorbing erriciency of the heat and moisture ~ -transferrer matrix 4.
On the other hand, ir the return air RA has an inordinately high humidity and the.outdoor air OA has an ;
extremely low temperature, or if the return air has a .. .
15 temperature 20C and a humidlty 75% and the outdoor :~ :
air has a temperature -20C and a humidity 100%, ~or example, the strai~ht line connecting the~~two points representing the return air and the outdoor alr in a ..
psychrometric chart in ~ig. 5 will intersect the ~ .
saturation line of relative humidity 100% at a point C ~
(13C) and a point D (-20C). Thus, when the return air .
RA and outdoor air OA are introduced into the heat and moisture transferring device 3, some portions of the air becomes higher than lOOg in humidity and below 0C in temperature~
so that the formation of frost occurs on the surfaces of the heat and moisture transferrer matrix 4. Combined with an increase in the resistance offered by the air passages to the streams of air, this causes a reduction in the performance of the heat and moisture transferring device 3.
3 As described hereinabove, the heat and moisture . ' 3 ~
- .-~' ....
. .
1 transferring device 3 has the disadvantage of being unable to recover heat, without causing any trouble, when the return air RA from the heated space and the outdoor air OA from the atmosphere have temperatures and humidities such that the straight line connecting the two points representing the two streams of air on a psychrometric shart intersects the saturation line, .because the formation of dew and frost occurs between these two points. In order to prevent the formation of dew and frost, proposals have hitherto been made to mount a preheater H, as shown in Fig. 3, in the air supply passage to be located in a position upstream of the heat and moisture transferring device 3, so as to preheat the outdoor air OA as shown in a solid line in Figs. 4 and 5 and convert the same into preheated outdoor air OA' which is caused to pass through the transferring device 3, in which the preheated outdoor air OA' is further heated by the heat recovered ~rom the return air RA from the heated space, so that the air will be introduced into the space as supply air SA.
However, the use of the preheater H has disadvantages in that, since it consumes eleçtricity, gas or other heating energy, the running cost is increased and control of .
operation becomes troublesome. An added disadvantage is that overall cost of production of the system is increased.
SUMMARY OF THE INVENTION
Accordingly, an object of the present invention is to provide a heat and moisture trans~erring system , , 8~
1 capable of preventing the formation of dew and frost on the surfaces of the heat and moisture transferring device, without requiring to use additional heating energy.
Another obJect of the present invention is to provide a heat and moisture transferring system adapted to effect transfer of heat and moisture between a stream of air supplied to an air-conditioned space and a stream of air returned from the air-conditioned space, wherein the outdoor air and the return air are preheated and precooled respectively by effecting heat exhcange therebetween through the agency of a heat transmitting medium before being passed through the heat and moisture transferring device, thereby preventing the formation .
15 of dew and frost on the surfaces of the heat and :~
moisture transferring device.
Another object of the invention is to provide a heat and moisture transferring system comprising a heat transmitting system inGluding a heat exchanger located in the air supply passage, a heat exchanger located in the air exhaust passage, and a conduit for interconnecting the two heat exchangers to form a closed circuit, so that the heat transmitting system can effect preheating and precooling of the outdoor air 25 and the return air respectively. ~:
Another ob~ect of the invention is to provide .
a heat and moisture transferring system which is pro- :.
vided with a double heat transmitting system so as to increase the heat recovery efficiency as compared with the heat and moisture transferring system using a .
~IL078~3Z0 - l single heat transmitting system.
A still another ob;ect of the invention is to provide a heat and moisture transferring system wherein a non-evaporative liquid is used as a heat transmitting medium circulated through the heat transmitting system whereby the heat transmitting system need not have a structure which can withstand high pressure and the construction of the system can be simplified.
A still another object of the invention is to provide a heat and moisture transferring system wherein a condensable gas which undergoes a change in phase when it effects exchange of heat is used as a heat transmitting medium circulated through the heat transmitting system, whereby latent heat of the heat transmitting medium can be utilized to increase the heat recovery efficiency.
Still another object of the invention is to provide a heat and moisture transferring system wherein the closed clrcuit of the heat transmitting system is formed as a gravity circulation circuit whereby the heat transmitting medium circulated through the closed circuit can be made to flow by gravity without requiring the use of power.
A further ob;ect of the invention is to provide a heat and moisture transferring system wherein the closed circuit is provided with means for forcedly circulating the heat transmitting medium therethrough whereby the heat exchangers can be arranged in any positions as desired without being subJected to any limitation as to their vertical relative positions.
A still further ob~ect of the invention is to ~. .
~ 6 --., ~0~8Z~
provide a heat and molsture transferrlng system ~hereln the heat transmitting system is composed of heat pipes wereby the construction of the system can be simplified and the heat transmitting medium can be made to flow ~ .
through the heat transmitting system without requiring ~
the use of power. :
A still further ob~ect of the invention is to . ~ .
provide a heat and moisture transferring system wherein an on-off valve is mounted in the closed circuit so that `
. . .
a condensable gas can be circulated through the closed :
clrcuit only when it is necessary to do so, particularly when the system is used in a heating mode.
A still further ob;ect of the invention is to .
provide a heat and moisture transferring system wherein means is provided to return, for recirculation, a ~ .
portion of the return air to the space to be heated, without being exhausted to the atmosphere as exhaust air in initial stage of starting of operation of the ' :
system in a heating mode in which the temperature of the :. :
return air is not very high.
...
7- - ~
~ ' Fig. 6 and Flg. 7 ea~h show an embodiment of the present invention. Referring to Fig. 6, there is shown a heat and moisture transferring system provided with a rotary type heat and moisture transferring . device 3 and comprising an air supply passage 1, and an air exhaust passage 2 disposed below the air supply passage 1, the two air passages 1 and 2 being partitioned by a partition wall 11 as shown in Fig. 12. The rotary type heat and moisture transferring device 3 is mounted ~-, . .
~78~2~ ~
1 in airtight fashion and located across the two air passages 1 and 2. The heat and moisture transferring system further comprises a heat transmitting system 5 including air heat exchangers 18 and 19 interconnected to form a closed circuit for a heat transmitting medium to be circulated therethrough between the two heat exchangers 18 and 19.
The construction of the heat and moisture transferring device 3 will be described in detail. As shown in Fig. 1, the device 3 comprises a rotary type heat and moisture transferrer matrix 4 rotatably mounted across the two air passages 1 and 2, a motor 7 for rotating the transferrer matrix ~ at a low rotational speed, e.g. 10 r.p.m., and a controller 8 for controlling the rotation of the motor 7. The heat and moisture transferrer matrix 4 comprises a disk-shaped air permeable body 6 rotatably supported by a shaft, not shown, and mounted within a panel casing 4c in such a manner that the opposite ends thereof face the respec-tive openings formed in the panel casing 4c. A parti-tion packing 10 transversely extending along the central portion o~ the air permeable body 6 supports the device 3 such that the lower portion of the air permeable body 6 is located in the air exhaust passage 2 and the upper portion thereof is located in the air supply passage 1 as shown in Fig. 6.
Referring to Fig. 1 again, the air permeable body 6 is connected to the motor through a belt 9 trained over the outer periphery of the body 6. Thus, any arbitrarily selected portion of the disk-shaped air -- : .: . . -, . ~ .
~t7~8~0 1 permeable body 6 is disposed in the air supply passage 1 during one half rotation of the body 6 and ln the air exhaust passage 2 during the other half rotation thereof.
The air permeable body 6 is formed of a sheet material having heat conductivity and moisture absorpti-vity, e.g. asbestos paper, and constructed in a manner to have a honeycomb structure comprising a multitude of air flow passages oriented axially of the air permeable body 6. The air permeable body 6 may, for exampleg be readily formed by winding, in roll form, a sheet of asbestos paper consisting of a plane member and a corrugated member both impregnated with a moisture absorbing agent, e.g. lithium chloride. -The rotary type heat and moisture transferring device 3 constructed as aforementioned is mounted in airtight fashion and located across the two air passages 1 and 2, as shown in Fig. 6. The downstream end of the air supply passage 1 opens in a room 14 through a heat exchanger 12 Or an air conditloner of the heat pump type and a supply fan 13, and the upstream end of the exhaust air passage 2 opens in the room 14 through a filter 15.
The upstream end of the air supply passage 1 opens in the atmosphere through a filter 16 and the downstr-eam end of the air exhaust passage 2 opens in the atmosphere through an exhaust fan 17.
The motor 7 is controlled by the operation controller 8 which comprises a relay circuit in which a timer, a relay and other control equipment are mounted.
Thus the controller 8 may have its operation ad~usted manually so that the motor 7 can be switched readily :
~L~7~ 0 1 from continuous rotation to a full stop or intermittent rotation as desired.
The construction of the heat transmitting system 5 will now be described. As aforesaid, the air heat exchangers 18 and 19 are mounted in the air supply passage 1 and the air exhaust passage 2 respectively in a manner to be located on the upstream side of the heat and moisture transferring device 3, so that heat exchange can be effected between the heat transmitting medium in the heat exchanger and the outdoor air OA
introduced into the system from the atmosphere and -between the heat transmitting medium and the return air RA from the heated room. More specifically, the heat exchanger 18 is disposed in a position higher than that of the other exchanger 19. The two heat exchangers 18 and 19 are interconnected at upper ends thereof by a piping 20 and at lower ends thereof by a piping 21 to form a closed circuit in which a suitable quantity of the heat transmitting medium is charged. The numeral 22 designates a drain pan located below the heat exchanger 19.
The heat transmitting system 5 is rendered operative only when the room 14 is to be heated. In this case, the heat exchanger 1~ located in the air supply passage 1 can be made to function as a radiator for warming the outdoor air OA introduced into the system, while the heat exchanger 19 located in the air exhaust passage 2 can be made to function as a heat receiver for absorbing heat from the return air RA
from the heated room 14.
78~
1 More specifically, if the heat transmitt~ng medium in the closed circuit is circulated in the direction of solid line arrows as shown in ~ig. 6, then the heat transmitting medium has its temperature raised by effecting heat exchange with the return air R~
immediately before the latter flows into the heat and moisture transferring device 3, and flows through the piping 20 into the heat exchaner 18 where the warmed heat transmitting medium effects heat exchange with the outdoor air OA immediately before the latter is intro~
duced into the heat and moisture transferring device 3, so that the outdoor air OA is warmed while the heat transmitting medium is cooled. By effecting the afore-mentioned heat exchanging operation cyclically, the outdoor air OA is preheated and becomes preheated outdoor air 0~' immediately before being introduced into the heat and moisture transferring device 3.
A condensable gas, e.g. chlorodifluoromethane (R-22), or non-evaporative, non-freezing liquid, e.g.
a solution of calcium chloride, may be used as the heat transmitting medium circulated through the heat trans-mitting system 5 However, when a non-freezing liquid is used, it is impossible to cause the liquid to flow in gravity circulation through the closed circuit, so that it becomes necessary to use a pump 23 for ~orcedly circulating the medium. On the other hand, when a condensable gas, e.g. dichlorodifluoromethane (R-12) or chlorodifluoromethane (R-22), is used, it will be evident that the heat exchanger 19 can be made to function as an evaporator and the heat exchanger 18 can be made .
~ ~t7~
1 to functlon as a condenser by arranging the air passage of lower air temperature or the air supply passage 1 at a higher level than the air passage of a higher air temperature or the exhaust alr passage 2 to enable the heat exchanger 18 to be located at a higher level than the heat exchanger 19. By this arrangement, it is possible to provide a circulation circuit suitable ~or a condensable gas which circulates in gravity circulation by changing its phase during circulation. It will be appreciated that the heat transmitting system 5 Or this form does not need any power for circulating the heat transmitting medium therethrough.
Additionally, if a non-evaporative liquid is used as the heat transmitting medium, the heat t~ansmitting system 5 need not have a structure which can withstand high pressure. This enables the construction of the system to be simplified. The use Or a condensable gas as the heat transmitting medium offers the advantage Or requiring the use of no power for circulating the medium as aforesaid. Moreover, since the use of a condensable gas makes it possible to utilize latent heat, the dif~erence between the temperature at which the medium condenses and the temperature at which the mediumm evaporates is small. This ofrers an advantage in that the heat recovery efriciency can be increased by increas-ing the difference between the temperature o~ return air RA and the evaporating temperature of the medium -, and the dirference between the temperature Or outdoor alr OA and the condensing temperature of the medium.
- 30 It ls to be understood that when a condensable gas is ~ - 13 -.4~
l used as the heat transmitting medium circulated through the heat transmitting system 5, the circulation of the gas can be effected not only in gravity circulation as illustrated in Fig. 6 but also in forced circulation -wherein a pump or compressor is used. If the circulation of the condensable medium is effected by khe latter system, no limits are set on the relative positions of the two heat exchangers 18 and 19, so that this offers the advantage of being able to design the arrangement of the air supply passage l and the air exhaust passage
Thls invention relates to a heat and moisture transferring system for effecting exchange of heat and moisture between two streams of air.
There have hitherto been known in the art two types of heat and moisture transferring devices, or devices of the rotary type and the static type, operat~ve to simultaneously effect heat exchange with respect to latent heat and sensible heat, thereby enabling heat to be recovered with a high degree of efficiency.
In one aspect of the present invention there is :~
provided a system for transferring heat and moisture between first and second air streams comprising, in combination: a first conduit means for said first air stream; a second conduit means for said second air stream; heat and moisture transferring means comprlsing a multitude of open-ended air passages defined by moisture absorptive and heat conductive material, a first set of :
said air passages being disposed in said first conduit -means for permitting said first air stream to pass .
thèrethrough and a second set of said air passages ;
being disposed in said second conduit means for permitting said second air stream to pass therethrough; means . :
- disposing the first and second set o air passages alternatively so that heat and moisture are transferred ..
between the first and second air streams passing through .
2S said passages through the moisture absorptive and heat conductive material; and a heat transmitting system including a first heat exchanging means disposed in said .~.
first condui.t means upstream of said heat and moisture transferring means for exchanging heat between said first air stream and a heat transmitting medium, a second heat exchanging means disposed in said second conduit means upstream of saia heat and molsture transferring means for exchanging heat ~etween sa;d second air stream and said heat transmltting medïum, and thîrd conduit means connecting said first and second heat exchanging means together for forming a closed circuit for said heat transmitting medium.
In the drawings illustrating the invention:
Fig. 1 is a perspective view, with certain parts being broken away, of a rotary type heat and mois-ture transferring device used in the heat and moisture transferri~g system according to the present invention;
Fig. 2 is a perspective view schematically showing essential portions of a static type heat and moisture transferring device used in the heat and moisture transferring system according to the invention;
Fig. 3 is a schematic view of a heat and moisture transferring system of the prior art;
Figs. 4 and 5 are psychrometric charts showing the relation between the temperature and the humidity of the air passing through the system shown in Fig. 3;
Fig. 6 is a schematic view of the heat and moisture transferring system comprising one embodiment of the invention;
Fig. 7 is a schematic view of another embodi-ment of the invention;
Fig. 8 is a psychrometric chart showing the I temperature-humidity characteristics of the embodiment shown in Fig. 6;
Fig. 9 is a graph showing the relation between the preheating ratio and the total heat recovery efficiency;
l 1 - l a-: ~ .
t7~2~
~ig. 10 ls a schematic view of still another embodiment of the invention;
Fig. 11 is a schematic view of a further embodiment of the invention; and Fig. 12 is a perspective view, with certain parts being broken away, of the embodiment shown in Fig. 6.
Fig. 1 shows a commonly used device of the rotary type. As shown, the heat and moisture transferring device 3 comprises a heat and moisture transferrer matrix 4 formed by winding, in roll rorm, a sheet of asbestos paper consisting of plane member and a corrugated member both impregnated with a moisture absorbing agent. As shown in :.
Fig. 3, the device 3 is mounted for rotation of the heat and moisture transferrer matrix 4 across an air supply pas- ~
sage 1 and an air exhaust passage 2 divided by a partition `.
wall 11 lnto upper and lower passages or left and right passages. One example of the rotary type heat and moisture transferring device is disclosed in US Patent `
No. 3,587,723. ~leanwhile Fig. 2 shows a commonly used heat and moisture transferring device of the static type comprising a plurality of corrugated members 4a of ~: ~
asbestos paper impregnated with a moisture absorbing ~ .
agent and a plurality of plane members 4b of the same material as the corrugated members 4a impregnated with :~
the same moisture absorbing agent, such corrugated members 4a and plane members 4b being mounted across the two air passages ln such a manner that they are -lb-~'7~ 20 l alternately piled in vertically stacked relationshlp so that the layers of the corrugated members 4a will intersect one another perpendicularly and the layers of the corrugated members 4a of odd numbers communicate with the air supply passage l while the layers of the corrugated members 4a of even numbers communicate with the air exhaust passage, for example. This type of device ~s disclosed in US Patent No. 3,666,oo7.
Assume that, when heating of a space is effected 10 in wintertime, such heat and moisture transferring device ~.
3 is used for recovering heat from return air RA from the heated space and exhausting the return air RA as exhaust air EA to the atmosphere, while the recovered heat is given to outdoor air OA which is introduced into the space as supply air SA. If the return air RA
has an inordinately high moisture content, or if, as shown in a psychrometric chart i.n Fig. 4, the outdoor air OA has a temperature 0C and a humidity 75% and the return air RA from the heated space has a temperature ~ :
20C and a humidity 95%, for example, the.straight line connecting the two points representing the outdoor air and return air in the chart will intersect the saturation line of relative humidity 100% at a point A
(17C) and a point B (5C). When this is the case, the return air RA will move downwardly along the broken line as it is being cooled by the heat and moisture transferring device 3 until its humidity becomes lQ0%
at the polnt A where it moves outwardly of the saturation line. The broken line will intersect the saturation line again at the point B. The return air is exhausted to ~.~q~38~
1 the atmosphere as exhaust air EA. When this phenomenon occurs, dew wlll be formed on the surfaces of the heat and moisture transferrer matrix 4 between the points A
and B, because the humidity o~ the return air RA is over 100% in this section of the broken line and the moisture in the return air RA condenses. The formation of dew on the sur~aces of the heat and moisture trans- ;:
.ferrer matrix 4 will cause effluence of the moisture absorbing agent, thereby causing a reduction in the ~ :
10 moisture absorbing erriciency of the heat and moisture ~ -transferrer matrix 4.
On the other hand, ir the return air RA has an inordinately high humidity and the.outdoor air OA has an ;
extremely low temperature, or if the return air has a .. .
15 temperature 20C and a humidlty 75% and the outdoor :~ :
air has a temperature -20C and a humidity 100%, ~or example, the strai~ht line connecting the~~two points representing the return air and the outdoor alr in a ..
psychrometric chart in ~ig. 5 will intersect the ~ .
saturation line of relative humidity 100% at a point C ~
(13C) and a point D (-20C). Thus, when the return air .
RA and outdoor air OA are introduced into the heat and moisture transferring device 3, some portions of the air becomes higher than lOOg in humidity and below 0C in temperature~
so that the formation of frost occurs on the surfaces of the heat and moisture transferrer matrix 4. Combined with an increase in the resistance offered by the air passages to the streams of air, this causes a reduction in the performance of the heat and moisture transferring device 3.
3 As described hereinabove, the heat and moisture . ' 3 ~
- .-~' ....
. .
1 transferring device 3 has the disadvantage of being unable to recover heat, without causing any trouble, when the return air RA from the heated space and the outdoor air OA from the atmosphere have temperatures and humidities such that the straight line connecting the two points representing the two streams of air on a psychrometric shart intersects the saturation line, .because the formation of dew and frost occurs between these two points. In order to prevent the formation of dew and frost, proposals have hitherto been made to mount a preheater H, as shown in Fig. 3, in the air supply passage to be located in a position upstream of the heat and moisture transferring device 3, so as to preheat the outdoor air OA as shown in a solid line in Figs. 4 and 5 and convert the same into preheated outdoor air OA' which is caused to pass through the transferring device 3, in which the preheated outdoor air OA' is further heated by the heat recovered ~rom the return air RA from the heated space, so that the air will be introduced into the space as supply air SA.
However, the use of the preheater H has disadvantages in that, since it consumes eleçtricity, gas or other heating energy, the running cost is increased and control of .
operation becomes troublesome. An added disadvantage is that overall cost of production of the system is increased.
SUMMARY OF THE INVENTION
Accordingly, an object of the present invention is to provide a heat and moisture trans~erring system , , 8~
1 capable of preventing the formation of dew and frost on the surfaces of the heat and moisture transferring device, without requiring to use additional heating energy.
Another obJect of the present invention is to provide a heat and moisture transferring system adapted to effect transfer of heat and moisture between a stream of air supplied to an air-conditioned space and a stream of air returned from the air-conditioned space, wherein the outdoor air and the return air are preheated and precooled respectively by effecting heat exhcange therebetween through the agency of a heat transmitting medium before being passed through the heat and moisture transferring device, thereby preventing the formation .
15 of dew and frost on the surfaces of the heat and :~
moisture transferring device.
Another object of the invention is to provide a heat and moisture transferring system comprising a heat transmitting system inGluding a heat exchanger located in the air supply passage, a heat exchanger located in the air exhaust passage, and a conduit for interconnecting the two heat exchangers to form a closed circuit, so that the heat transmitting system can effect preheating and precooling of the outdoor air 25 and the return air respectively. ~:
Another ob~ect of the invention is to provide .
a heat and moisture transferring system which is pro- :.
vided with a double heat transmitting system so as to increase the heat recovery efficiency as compared with the heat and moisture transferring system using a .
~IL078~3Z0 - l single heat transmitting system.
A still another ob;ect of the invention is to provide a heat and moisture transferring system wherein a non-evaporative liquid is used as a heat transmitting medium circulated through the heat transmitting system whereby the heat transmitting system need not have a structure which can withstand high pressure and the construction of the system can be simplified.
A still another object of the invention is to provide a heat and moisture transferring system wherein a condensable gas which undergoes a change in phase when it effects exchange of heat is used as a heat transmitting medium circulated through the heat transmitting system, whereby latent heat of the heat transmitting medium can be utilized to increase the heat recovery efficiency.
Still another object of the invention is to provide a heat and moisture transferring system wherein the closed clrcuit of the heat transmitting system is formed as a gravity circulation circuit whereby the heat transmitting medium circulated through the closed circuit can be made to flow by gravity without requiring the use of power.
A further ob;ect of the invention is to provide a heat and moisture transferring system wherein the closed circuit is provided with means for forcedly circulating the heat transmitting medium therethrough whereby the heat exchangers can be arranged in any positions as desired without being subJected to any limitation as to their vertical relative positions.
A still further ob~ect of the invention is to ~. .
~ 6 --., ~0~8Z~
provide a heat and molsture transferrlng system ~hereln the heat transmitting system is composed of heat pipes wereby the construction of the system can be simplified and the heat transmitting medium can be made to flow ~ .
through the heat transmitting system without requiring ~
the use of power. :
A still further ob~ect of the invention is to . ~ .
provide a heat and moisture transferring system wherein an on-off valve is mounted in the closed circuit so that `
. . .
a condensable gas can be circulated through the closed :
clrcuit only when it is necessary to do so, particularly when the system is used in a heating mode.
A still further ob;ect of the invention is to .
provide a heat and moisture transferring system wherein means is provided to return, for recirculation, a ~ .
portion of the return air to the space to be heated, without being exhausted to the atmosphere as exhaust air in initial stage of starting of operation of the ' :
system in a heating mode in which the temperature of the :. :
return air is not very high.
...
7- - ~
~ ' Fig. 6 and Flg. 7 ea~h show an embodiment of the present invention. Referring to Fig. 6, there is shown a heat and moisture transferring system provided with a rotary type heat and moisture transferring . device 3 and comprising an air supply passage 1, and an air exhaust passage 2 disposed below the air supply passage 1, the two air passages 1 and 2 being partitioned by a partition wall 11 as shown in Fig. 12. The rotary type heat and moisture transferring device 3 is mounted ~-, . .
~78~2~ ~
1 in airtight fashion and located across the two air passages 1 and 2. The heat and moisture transferring system further comprises a heat transmitting system 5 including air heat exchangers 18 and 19 interconnected to form a closed circuit for a heat transmitting medium to be circulated therethrough between the two heat exchangers 18 and 19.
The construction of the heat and moisture transferring device 3 will be described in detail. As shown in Fig. 1, the device 3 comprises a rotary type heat and moisture transferrer matrix 4 rotatably mounted across the two air passages 1 and 2, a motor 7 for rotating the transferrer matrix ~ at a low rotational speed, e.g. 10 r.p.m., and a controller 8 for controlling the rotation of the motor 7. The heat and moisture transferrer matrix 4 comprises a disk-shaped air permeable body 6 rotatably supported by a shaft, not shown, and mounted within a panel casing 4c in such a manner that the opposite ends thereof face the respec-tive openings formed in the panel casing 4c. A parti-tion packing 10 transversely extending along the central portion o~ the air permeable body 6 supports the device 3 such that the lower portion of the air permeable body 6 is located in the air exhaust passage 2 and the upper portion thereof is located in the air supply passage 1 as shown in Fig. 6.
Referring to Fig. 1 again, the air permeable body 6 is connected to the motor through a belt 9 trained over the outer periphery of the body 6. Thus, any arbitrarily selected portion of the disk-shaped air -- : .: . . -, . ~ .
~t7~8~0 1 permeable body 6 is disposed in the air supply passage 1 during one half rotation of the body 6 and ln the air exhaust passage 2 during the other half rotation thereof.
The air permeable body 6 is formed of a sheet material having heat conductivity and moisture absorpti-vity, e.g. asbestos paper, and constructed in a manner to have a honeycomb structure comprising a multitude of air flow passages oriented axially of the air permeable body 6. The air permeable body 6 may, for exampleg be readily formed by winding, in roll form, a sheet of asbestos paper consisting of a plane member and a corrugated member both impregnated with a moisture absorbing agent, e.g. lithium chloride. -The rotary type heat and moisture transferring device 3 constructed as aforementioned is mounted in airtight fashion and located across the two air passages 1 and 2, as shown in Fig. 6. The downstream end of the air supply passage 1 opens in a room 14 through a heat exchanger 12 Or an air conditloner of the heat pump type and a supply fan 13, and the upstream end of the exhaust air passage 2 opens in the room 14 through a filter 15.
The upstream end of the air supply passage 1 opens in the atmosphere through a filter 16 and the downstr-eam end of the air exhaust passage 2 opens in the atmosphere through an exhaust fan 17.
The motor 7 is controlled by the operation controller 8 which comprises a relay circuit in which a timer, a relay and other control equipment are mounted.
Thus the controller 8 may have its operation ad~usted manually so that the motor 7 can be switched readily :
~L~7~ 0 1 from continuous rotation to a full stop or intermittent rotation as desired.
The construction of the heat transmitting system 5 will now be described. As aforesaid, the air heat exchangers 18 and 19 are mounted in the air supply passage 1 and the air exhaust passage 2 respectively in a manner to be located on the upstream side of the heat and moisture transferring device 3, so that heat exchange can be effected between the heat transmitting medium in the heat exchanger and the outdoor air OA
introduced into the system from the atmosphere and -between the heat transmitting medium and the return air RA from the heated room. More specifically, the heat exchanger 18 is disposed in a position higher than that of the other exchanger 19. The two heat exchangers 18 and 19 are interconnected at upper ends thereof by a piping 20 and at lower ends thereof by a piping 21 to form a closed circuit in which a suitable quantity of the heat transmitting medium is charged. The numeral 22 designates a drain pan located below the heat exchanger 19.
The heat transmitting system 5 is rendered operative only when the room 14 is to be heated. In this case, the heat exchanger 1~ located in the air supply passage 1 can be made to function as a radiator for warming the outdoor air OA introduced into the system, while the heat exchanger 19 located in the air exhaust passage 2 can be made to function as a heat receiver for absorbing heat from the return air RA
from the heated room 14.
78~
1 More specifically, if the heat transmitt~ng medium in the closed circuit is circulated in the direction of solid line arrows as shown in ~ig. 6, then the heat transmitting medium has its temperature raised by effecting heat exchange with the return air R~
immediately before the latter flows into the heat and moisture transferring device 3, and flows through the piping 20 into the heat exchaner 18 where the warmed heat transmitting medium effects heat exchange with the outdoor air OA immediately before the latter is intro~
duced into the heat and moisture transferring device 3, so that the outdoor air OA is warmed while the heat transmitting medium is cooled. By effecting the afore-mentioned heat exchanging operation cyclically, the outdoor air OA is preheated and becomes preheated outdoor air 0~' immediately before being introduced into the heat and moisture transferring device 3.
A condensable gas, e.g. chlorodifluoromethane (R-22), or non-evaporative, non-freezing liquid, e.g.
a solution of calcium chloride, may be used as the heat transmitting medium circulated through the heat trans-mitting system 5 However, when a non-freezing liquid is used, it is impossible to cause the liquid to flow in gravity circulation through the closed circuit, so that it becomes necessary to use a pump 23 for ~orcedly circulating the medium. On the other hand, when a condensable gas, e.g. dichlorodifluoromethane (R-12) or chlorodifluoromethane (R-22), is used, it will be evident that the heat exchanger 19 can be made to function as an evaporator and the heat exchanger 18 can be made .
~ ~t7~
1 to functlon as a condenser by arranging the air passage of lower air temperature or the air supply passage 1 at a higher level than the air passage of a higher air temperature or the exhaust alr passage 2 to enable the heat exchanger 18 to be located at a higher level than the heat exchanger 19. By this arrangement, it is possible to provide a circulation circuit suitable ~or a condensable gas which circulates in gravity circulation by changing its phase during circulation. It will be appreciated that the heat transmitting system 5 Or this form does not need any power for circulating the heat transmitting medium therethrough.
Additionally, if a non-evaporative liquid is used as the heat transmitting medium, the heat t~ansmitting system 5 need not have a structure which can withstand high pressure. This enables the construction of the system to be simplified. The use Or a condensable gas as the heat transmitting medium offers the advantage Or requiring the use of no power for circulating the medium as aforesaid. Moreover, since the use of a condensable gas makes it possible to utilize latent heat, the dif~erence between the temperature at which the medium condenses and the temperature at which the mediumm evaporates is small. This ofrers an advantage in that the heat recovery efriciency can be increased by increas-ing the difference between the temperature o~ return air RA and the evaporating temperature of the medium -, and the dirference between the temperature Or outdoor alr OA and the condensing temperature of the medium.
- 30 It ls to be understood that when a condensable gas is ~ - 13 -.4~
l used as the heat transmitting medium circulated through the heat transmitting system 5, the circulation of the gas can be effected not only in gravity circulation as illustrated in Fig. 6 but also in forced circulation -wherein a pump or compressor is used. If the circulation of the condensable medium is effected by khe latter system, no limits are set on the relative positions of the two heat exchangers 18 and 19, so that this offers the advantage of being able to design the arrangement of the air supply passage l and the air exhaust passage
2 as desired.
The operation of the heat and moisture trans-ferring system shown in Flg. 6 will be described with reference to the case in which R-22 is charged in the heat transmitting system 5 and circulated in gravity circulation therethrough. When the room 14 is to be heated in the wintertime, the air conditioner is operated in a heating mode so that the supply air SA is heated by the heat exchanger 12 which functions as a condenser.
The heat and moisture transferrer matrix 4 of the heat and moisture transferring device 3 is rotated at a predetermined number of revolutions. The return air RA
of high temperature and high moisture content from the heated room 14 is filtered by the filter 15 and brought i.nto contact with the heat exchanger l9. The return air RA effects heat exchange ~ith the refrigerant R-22 in the heat exchanger l9, with the result that the former is cooled and has its moisture content reduced, becoming precooled return air RA~. Since the temperature of the refrigerant is lower than the dew point of the 1~7~ 0 1 return air RA, the moisture content of the return air RA
is reduced. The precooled return air RA' flows into the half portion of the heat and moisture transferrer matrix 4 disposed in the air exhaust passage 2, where the moisture and heat in the precooled return air RA' are absorbed by the air permeable body 6. Thereafter the air is exhausted as exhaust air EA to the atmosphere.
Meanwhile the refrigerant R-22 in the heat exchanger 19 is evaporated by the heat of the return air RA and flows in a gaseous state into the heat exchanger 18. The portion of the air permeable body 6 of the heat and . .
moisture transferrer matrix 4, which has absorbed heat and moisture from the return air, rotates and moves ~.-.
into the air supply passage 1.
15Outdoor air OA of low temperature and low moisture content is filtered by the filter 16 and effects heat exchange with the refrigerant ~-22 in the gaseous state in the heat exchanger 18, with the result that the outdoor air OA is heated and becomes preheated outdoor air OA'. The preheated outdoor air OA' ~lows through the half portion of the heat and moisture trans-ferrer matrix 4 which is disposed in the air supply passage 1, so that it is heated and has its moisture ~.
content increased by the air permeable body 6. There-after the outdoor air OA is heated to a predetermined temperature in the heat exchanger 12 before being deli~-ered to the room 14. Meanwhile the refrigerant in the gaseous state in the heat exchanger 18 is condensed and : -and changes to a liquid state, and the refrigerant in the liquid state flow downwardly by its own weight into - 15 - ~ ~
, . : :
978~ Q
1 the heat exchanger 19 which is disposed at a lower level than the heat exchanger 18. The portion of the air permeable body 6 from which heat and moisture have been absorbed by the outdoor air OA rotates into the exhaust air passage 2. The aforesaid cycle of operation is repeated so that the heat and moisture in the return air are continuously transferred to the outdoor alr. The amount of precooling and preheating the return air and the outdoor air respectively ~ill be described later.
When a cooling operation is performed in the summertime, the air conditioner is operated in a cooling mode so that the heat exchanger 12 functions as an evaporator and cools the supply air SA. The heat and moisture transferrer matrix 4 of the heat and moisture transferring device 3 is rotated at a predetermined number of revolutions. In this case, the outdoor air is higher in temperature than the return air, so that no gravity circulation of the refrigerant takes place in the heat transmitting system 5. Thus the heat trans-mitting system 5 is rendered inoperative and the transferof heat between the return air and the outdoor air through the agency of the refrigerant does not take place.
However, since the heat and moisture transferrer matrix 4 of the heat and moisture transferring device 3 rotates, the heat and moisture in the outdoor air of high temperature and high moisture content are transferred to the return air through the heat and moisture trans-ferring device 3. That is, the outdoor air of high temperature and high moisture content is cooled and has its moisture content reduced by the return air of ~07~ Z~I
1 relatively low temperature and low moisture content, and then cooled to a predetermined temperature by the -~eat exchanger 12 before being delivered to the room 14.
In this case, under general temperature and humidity conditions of sapce cooling, the straight line connecting the points representing the temperatures and humidities -of the outdoor air OA and the return air RA in a psychro-metric chart does not intersect the saturation line of relative humidity 100%, so that no dew formation occurs in the heat and moisture transferring device 3. Thus no trouble occurs even if the heat transmitting sys~em 5 is rendered inoperative as aforesaid.
There is no need to heat or cool outdoor air in the seasons between summer and winter, so that the air conditioner has only to perform a ventilating operation. ~herefore, it is not necessary to rotate the heat and moisture transferrer matrix 4 of the heat and moisture transferring device 3. However, in case the heat and moisture transferring device 3 is shut -down, dew formation on the surfaces of the air permeable body 6 or other trouble may occur. Therefore, it is desirable that the motor operation controller 8 be actuated, so that the heat and moisture transferrer matrix 4 will be rotated intermittently for several minutes at intervals of 30 to 60 minutes, at a rota-tional speed of 10 r.p.m. or less, for example. This eliminates the trouble of effluence of the moisture absorbing agent due to the formation of dew therein and obturation of the air flow passages with dust in the heat and moisture transferrer matrix 4.
.
1~715 13ZO
1 The recovery of` heat that is effected when a heat and moisture transferring operation is per~ormed in the wintertime as aforesaid will be further discussed.
For example, when the heat and moisture transferring device 3 alone is used in places of lntense cold, the moisture in the return air RA from which heat is recovered will cause the formation of dew or frost in the heat and moisture transferring device 3 and troubIe will result, if the return air RA has an abnormally 0 high moisture content and the outdoor air OA has an extremely low temperature.
In the present invention, the heat transmit ting system 5 including the heat exchangers 18 and 19 are used in combination with the heat and moisture transferring device 3 as aforesaid. Thus, by designing the heat and moisture transferring device 3 and the heat exchangers 18 and 19 in a manner to have suitable heat exchanging capacities, the formation of dew and frost can be prevented.
~ore specifically, the heat and moisture transferring device 3 and the heat exchangers 18 and 19 should be designed in such a manner that the straight line connecting the points representing the temperatures and humidities of precooled return air RA' obtained by precooling return air RA from the room 14 by the heat exchanger 19 and of preheated outdoor air OA' obtained by preheating outdoor air OA by the heat exchanger 18 lies inwardly of the saturation line as shown in Fig. 8.
This enables dew and frost formation to be prevented.
This ls one of the important features of the invention.
- ~ILC;788~(J
1 This feature will be described in detail with reference to Figs. 6, 8 and 9. Assume that the outdoor air OA has a temperature -20C and a humi.dity 100% and the return air RA has a temperature 20C and a humidity 75%. Then it will be seen that the straight line connecting the points representing the temperatures and humidities of the preheated outdoor air OA' (passed through the heat exchanger 18) having a temperature -6C
and a humidity 35% and of the precooled return air RA' (passed through the heat exchanger 19) having a tempera-ture 13C and a humidity 90% on the psychrometric chart in Fig. 8 does not intersect the saturation line of relative humidity 100%n That is, by designing the heat . .
exchanger 19 functioning as an evaporator in such a 15 manner that its evaporating temperature (Tc) becomes .
higher than 0C, the return air RA of 20C beco~es precooled return air RA' of 13C which is cooled to a temperature range higher than the evaporating tempera- .
ture (Tc), and the outdoor air OA of -20C is heated and changed into the preheated outdoor air OA' of -6C
by the heat exchanger 18 which functions as a condenser of a condensing temperature which is substantially equal to the evaporating temperature (Tc). Meanwhile the precooled return air RA' of 13C is further cooled at the heat and moisture transferring device 3 and changed into exhaust air EA of -1C which is exhausted to the atmosphere, and the preheated outdoor air OA' of -6C is :
further heated at the heat and moisture transferring device 3 and changed back into supply air SA of 8C which is introduced into the room 1 .
3L0~8~3Z(~
1 Thus the return air RA of 20C is changed into the exhaust air EA of -1C, and the heat difference between the return air RA and the exhaust air EA is recovered by the system according to the invention.
The recovered heat is used for heating the outdoor air of -20C and changing the same into the supply air SA of 8C for introduction into the room 14 to be heated.
It will be apparent that the system according to the invention has a very high efficiency in recovering and transferring heat from one air stream to the other air stream.
The state of air passing through the heat and moisture transferring device 3 at this time will be further discussed. It will be seen that the straight line connecting the points representing the precooled return air RA', supply air SA, exhaust air EA and;pre-heated outdoor air OA t in a psychrometric chart does not intersect the saturation line as shown in Fig. 8.
Accordingly, it will be apparent that, if the 2~ heat and moisture transferring device 3 is used in combination wlth the heat transmitting system 5 includ-ing the heat exchangers 18 and 19 and if the heat exchan-gers 18 and 19 are each designed in a manner to have a suitable heat exchanging capacity, then it is possible to enable the heat and ~oisture transferring device 3 to function normally without dew and frost being formed on the surfaces of the heat and moisture transferrer matrix 4, even if the system according to the invention operates under conditions such that the return air RA has an 71!382~
inordinately high humidity while the outdoor air OA has an extremely low temperature-conditions under which the formation of dew and frost tends to occur.
A comparison of the heat and moisture transferring system according to the invention wherein the heat transmit-ting system 5 is combined with the heat and moisture trans-ferring device 3 with a conventional system wherein the out-door air entering the heat and moisture transferring device 3 is heated by an electric heater, gas burner or other separate heating source shows that the use of the heat transmitting system S enables to achieve a higher heat recovery efficiency.
More specifically, the total heat recovery effi-ciency n of the heat and moisture transferring devicë 3 and the heat transmitting system 5 can be expressed by the ollow-ing formula:
il +Q i2 ~ i4where ~ il: Heat gain through heat transmi~ing system 5.
~ i2: Heat gain through heat and moisture trans-ferring device 3.
i4: The difference in enthalpy between return air RA and outdoor air OA. - .
If the values of~ il and~ i4 are calculated in the psychrometric chart shown in Fig. 8,h il/~ i4 = 0~2.
Suppose that the heat and moisture transferring device 3 is designed to operate at 70~ of heat recovery effi-ciency. The heat recovery efficiency of the heat and moisture transferring device 3 can be expressed as follows:
The difference in enthalPY between OA' and SA
The difference in enthalpy between OA' and RA' The difference in enthalpy between EA and RA' The difference in enthalpy between OAI and RA~
. , ' .' ' ~ , ~i2 ~i4 - 2 ~il 0'7 Thus~ Qi2 = 0 7 ( Qi4 2 ~
The total heat recovery efficiency can be calculated as follows;
~i 1 + Qi2 n= ~i4 ~ 0.7 ( ~ 2 Ail) = ~i4 = 0.2 + 0.7 (1 - 2 x 0.2) = 0.62 On the other hand, in a conventional system of the external heating type r~herein the heat gain ~ih is obtained by means of a separate heat source, such as an electric heater or gas burner, the total heat recovery efficiency n ~ can be cal-culated as follows as shown in the psychrometric chart of ~ig. 5:
~i 0 7 ( bi - ai ) i4 - = 0.7 x (1- 0.2) = 0.56 Also, if ~il/ ai4 = ~ = 0.3 un~er conditions of different temperature and humidity other than those shown in Fig. 8 and Fig. 5, n = 0~58 and n ' = 0.49 are ca~culated.
The total heat recovery efficiency is plotted in Fig. 9 against the preheating ratio ~il/ ai4 or ~ which is varied by changing the conditions of temperatures and humidity with respect to the system according to the invention , wherein preheating of outdoor air is effected by means of the heat transmitting system and a system of the prior art using an external heat source for preheating outdoor air. In Fig. 9, it will be clearly seen that n > ~ ~ . This shows that the system according to the invention is higher in total heat recovery efficiency than the system of the prior art ~ .
~, . .
7882(~
' 1 using a separate heat source, such as an electric,heater or gas burner. Moreover, the present invention offers an additional advanta~e in that the energy ~or pre-heatlng outdoor air can be done without.
Example Experiments were conducted on the heat and moisture trans~erring system according to the invention to determine whether the formation of dew and/or frost occurs under varying cond1tions.-- The conditions under which the experiments were conducted are as follows:
''~' ' "
Table 1 . :, Conditions Conditions No. of Rows of No. of Rows of Outdoor of Return Heat Exchanging Tubes of Heat Ex-Air OA Air RA in the Heat Exchanger changer 18 , on OA Side . .
_30C 20C 13 ~~ 6 - (1) RH: }00~ RH: 75% (286 mm)(132 mm) '~
.
- -20C 20~C 4 4 (2) RH: 100~ RH: 75~ (38 mm) (88 mm) . .
The operation of the heat and moisture trans-ferring system shown in Flg. 6 will be described with reference to the case in which R-22 is charged in the heat transmitting system 5 and circulated in gravity circulation therethrough. When the room 14 is to be heated in the wintertime, the air conditioner is operated in a heating mode so that the supply air SA is heated by the heat exchanger 12 which functions as a condenser.
The heat and moisture transferrer matrix 4 of the heat and moisture transferring device 3 is rotated at a predetermined number of revolutions. The return air RA
of high temperature and high moisture content from the heated room 14 is filtered by the filter 15 and brought i.nto contact with the heat exchanger l9. The return air RA effects heat exchange ~ith the refrigerant R-22 in the heat exchanger l9, with the result that the former is cooled and has its moisture content reduced, becoming precooled return air RA~. Since the temperature of the refrigerant is lower than the dew point of the 1~7~ 0 1 return air RA, the moisture content of the return air RA
is reduced. The precooled return air RA' flows into the half portion of the heat and moisture transferrer matrix 4 disposed in the air exhaust passage 2, where the moisture and heat in the precooled return air RA' are absorbed by the air permeable body 6. Thereafter the air is exhausted as exhaust air EA to the atmosphere.
Meanwhile the refrigerant R-22 in the heat exchanger 19 is evaporated by the heat of the return air RA and flows in a gaseous state into the heat exchanger 18. The portion of the air permeable body 6 of the heat and . .
moisture transferrer matrix 4, which has absorbed heat and moisture from the return air, rotates and moves ~.-.
into the air supply passage 1.
15Outdoor air OA of low temperature and low moisture content is filtered by the filter 16 and effects heat exchange with the refrigerant ~-22 in the gaseous state in the heat exchanger 18, with the result that the outdoor air OA is heated and becomes preheated outdoor air OA'. The preheated outdoor air OA' ~lows through the half portion of the heat and moisture trans-ferrer matrix 4 which is disposed in the air supply passage 1, so that it is heated and has its moisture ~.
content increased by the air permeable body 6. There-after the outdoor air OA is heated to a predetermined temperature in the heat exchanger 12 before being deli~-ered to the room 14. Meanwhile the refrigerant in the gaseous state in the heat exchanger 18 is condensed and : -and changes to a liquid state, and the refrigerant in the liquid state flow downwardly by its own weight into - 15 - ~ ~
, . : :
978~ Q
1 the heat exchanger 19 which is disposed at a lower level than the heat exchanger 18. The portion of the air permeable body 6 from which heat and moisture have been absorbed by the outdoor air OA rotates into the exhaust air passage 2. The aforesaid cycle of operation is repeated so that the heat and moisture in the return air are continuously transferred to the outdoor alr. The amount of precooling and preheating the return air and the outdoor air respectively ~ill be described later.
When a cooling operation is performed in the summertime, the air conditioner is operated in a cooling mode so that the heat exchanger 12 functions as an evaporator and cools the supply air SA. The heat and moisture transferrer matrix 4 of the heat and moisture transferring device 3 is rotated at a predetermined number of revolutions. In this case, the outdoor air is higher in temperature than the return air, so that no gravity circulation of the refrigerant takes place in the heat transmitting system 5. Thus the heat trans-mitting system 5 is rendered inoperative and the transferof heat between the return air and the outdoor air through the agency of the refrigerant does not take place.
However, since the heat and moisture transferrer matrix 4 of the heat and moisture transferring device 3 rotates, the heat and moisture in the outdoor air of high temperature and high moisture content are transferred to the return air through the heat and moisture trans-ferring device 3. That is, the outdoor air of high temperature and high moisture content is cooled and has its moisture content reduced by the return air of ~07~ Z~I
1 relatively low temperature and low moisture content, and then cooled to a predetermined temperature by the -~eat exchanger 12 before being delivered to the room 14.
In this case, under general temperature and humidity conditions of sapce cooling, the straight line connecting the points representing the temperatures and humidities -of the outdoor air OA and the return air RA in a psychro-metric chart does not intersect the saturation line of relative humidity 100%, so that no dew formation occurs in the heat and moisture transferring device 3. Thus no trouble occurs even if the heat transmitting sys~em 5 is rendered inoperative as aforesaid.
There is no need to heat or cool outdoor air in the seasons between summer and winter, so that the air conditioner has only to perform a ventilating operation. ~herefore, it is not necessary to rotate the heat and moisture transferrer matrix 4 of the heat and moisture transferring device 3. However, in case the heat and moisture transferring device 3 is shut -down, dew formation on the surfaces of the air permeable body 6 or other trouble may occur. Therefore, it is desirable that the motor operation controller 8 be actuated, so that the heat and moisture transferrer matrix 4 will be rotated intermittently for several minutes at intervals of 30 to 60 minutes, at a rota-tional speed of 10 r.p.m. or less, for example. This eliminates the trouble of effluence of the moisture absorbing agent due to the formation of dew therein and obturation of the air flow passages with dust in the heat and moisture transferrer matrix 4.
.
1~715 13ZO
1 The recovery of` heat that is effected when a heat and moisture transferring operation is per~ormed in the wintertime as aforesaid will be further discussed.
For example, when the heat and moisture transferring device 3 alone is used in places of lntense cold, the moisture in the return air RA from which heat is recovered will cause the formation of dew or frost in the heat and moisture transferring device 3 and troubIe will result, if the return air RA has an abnormally 0 high moisture content and the outdoor air OA has an extremely low temperature.
In the present invention, the heat transmit ting system 5 including the heat exchangers 18 and 19 are used in combination with the heat and moisture transferring device 3 as aforesaid. Thus, by designing the heat and moisture transferring device 3 and the heat exchangers 18 and 19 in a manner to have suitable heat exchanging capacities, the formation of dew and frost can be prevented.
~ore specifically, the heat and moisture transferring device 3 and the heat exchangers 18 and 19 should be designed in such a manner that the straight line connecting the points representing the temperatures and humidities of precooled return air RA' obtained by precooling return air RA from the room 14 by the heat exchanger 19 and of preheated outdoor air OA' obtained by preheating outdoor air OA by the heat exchanger 18 lies inwardly of the saturation line as shown in Fig. 8.
This enables dew and frost formation to be prevented.
This ls one of the important features of the invention.
- ~ILC;788~(J
1 This feature will be described in detail with reference to Figs. 6, 8 and 9. Assume that the outdoor air OA has a temperature -20C and a humi.dity 100% and the return air RA has a temperature 20C and a humidity 75%. Then it will be seen that the straight line connecting the points representing the temperatures and humidities of the preheated outdoor air OA' (passed through the heat exchanger 18) having a temperature -6C
and a humidity 35% and of the precooled return air RA' (passed through the heat exchanger 19) having a tempera-ture 13C and a humidity 90% on the psychrometric chart in Fig. 8 does not intersect the saturation line of relative humidity 100%n That is, by designing the heat . .
exchanger 19 functioning as an evaporator in such a 15 manner that its evaporating temperature (Tc) becomes .
higher than 0C, the return air RA of 20C beco~es precooled return air RA' of 13C which is cooled to a temperature range higher than the evaporating tempera- .
ture (Tc), and the outdoor air OA of -20C is heated and changed into the preheated outdoor air OA' of -6C
by the heat exchanger 18 which functions as a condenser of a condensing temperature which is substantially equal to the evaporating temperature (Tc). Meanwhile the precooled return air RA' of 13C is further cooled at the heat and moisture transferring device 3 and changed into exhaust air EA of -1C which is exhausted to the atmosphere, and the preheated outdoor air OA' of -6C is :
further heated at the heat and moisture transferring device 3 and changed back into supply air SA of 8C which is introduced into the room 1 .
3L0~8~3Z(~
1 Thus the return air RA of 20C is changed into the exhaust air EA of -1C, and the heat difference between the return air RA and the exhaust air EA is recovered by the system according to the invention.
The recovered heat is used for heating the outdoor air of -20C and changing the same into the supply air SA of 8C for introduction into the room 14 to be heated.
It will be apparent that the system according to the invention has a very high efficiency in recovering and transferring heat from one air stream to the other air stream.
The state of air passing through the heat and moisture transferring device 3 at this time will be further discussed. It will be seen that the straight line connecting the points representing the precooled return air RA', supply air SA, exhaust air EA and;pre-heated outdoor air OA t in a psychrometric chart does not intersect the saturation line as shown in Fig. 8.
Accordingly, it will be apparent that, if the 2~ heat and moisture transferring device 3 is used in combination wlth the heat transmitting system 5 includ-ing the heat exchangers 18 and 19 and if the heat exchan-gers 18 and 19 are each designed in a manner to have a suitable heat exchanging capacity, then it is possible to enable the heat and ~oisture transferring device 3 to function normally without dew and frost being formed on the surfaces of the heat and moisture transferrer matrix 4, even if the system according to the invention operates under conditions such that the return air RA has an 71!382~
inordinately high humidity while the outdoor air OA has an extremely low temperature-conditions under which the formation of dew and frost tends to occur.
A comparison of the heat and moisture transferring system according to the invention wherein the heat transmit-ting system 5 is combined with the heat and moisture trans-ferring device 3 with a conventional system wherein the out-door air entering the heat and moisture transferring device 3 is heated by an electric heater, gas burner or other separate heating source shows that the use of the heat transmitting system S enables to achieve a higher heat recovery efficiency.
More specifically, the total heat recovery effi-ciency n of the heat and moisture transferring devicë 3 and the heat transmitting system 5 can be expressed by the ollow-ing formula:
il +Q i2 ~ i4where ~ il: Heat gain through heat transmi~ing system 5.
~ i2: Heat gain through heat and moisture trans-ferring device 3.
i4: The difference in enthalpy between return air RA and outdoor air OA. - .
If the values of~ il and~ i4 are calculated in the psychrometric chart shown in Fig. 8,h il/~ i4 = 0~2.
Suppose that the heat and moisture transferring device 3 is designed to operate at 70~ of heat recovery effi-ciency. The heat recovery efficiency of the heat and moisture transferring device 3 can be expressed as follows:
The difference in enthalPY between OA' and SA
The difference in enthalpy between OA' and RA' The difference in enthalpy between EA and RA' The difference in enthalpy between OAI and RA~
. , ' .' ' ~ , ~i2 ~i4 - 2 ~il 0'7 Thus~ Qi2 = 0 7 ( Qi4 2 ~
The total heat recovery efficiency can be calculated as follows;
~i 1 + Qi2 n= ~i4 ~ 0.7 ( ~ 2 Ail) = ~i4 = 0.2 + 0.7 (1 - 2 x 0.2) = 0.62 On the other hand, in a conventional system of the external heating type r~herein the heat gain ~ih is obtained by means of a separate heat source, such as an electric heater or gas burner, the total heat recovery efficiency n ~ can be cal-culated as follows as shown in the psychrometric chart of ~ig. 5:
~i 0 7 ( bi - ai ) i4 - = 0.7 x (1- 0.2) = 0.56 Also, if ~il/ ai4 = ~ = 0.3 un~er conditions of different temperature and humidity other than those shown in Fig. 8 and Fig. 5, n = 0~58 and n ' = 0.49 are ca~culated.
The total heat recovery efficiency is plotted in Fig. 9 against the preheating ratio ~il/ ai4 or ~ which is varied by changing the conditions of temperatures and humidity with respect to the system according to the invention , wherein preheating of outdoor air is effected by means of the heat transmitting system and a system of the prior art using an external heat source for preheating outdoor air. In Fig. 9, it will be clearly seen that n > ~ ~ . This shows that the system according to the invention is higher in total heat recovery efficiency than the system of the prior art ~ .
~, . .
7882(~
' 1 using a separate heat source, such as an electric,heater or gas burner. Moreover, the present invention offers an additional advanta~e in that the energy ~or pre-heatlng outdoor air can be done without.
Example Experiments were conducted on the heat and moisture trans~erring system according to the invention to determine whether the formation of dew and/or frost occurs under varying cond1tions.-- The conditions under which the experiments were conducted are as follows:
''~' ' "
Table 1 . :, Conditions Conditions No. of Rows of No. of Rows of Outdoor of Return Heat Exchanging Tubes of Heat Ex-Air OA Air RA in the Heat Exchanger changer 18 , on OA Side . .
_30C 20C 13 ~~ 6 - (1) RH: }00~ RH: 75% (286 mm)(132 mm) '~
.
- -20C 20~C 4 4 (2) RH: 100~ RH: 75~ (38 mm) (88 mm) . .
(3) RH: 100% RH: 75% tllO mm)(66 mm) Note: In the above table, RH stands for relative humidity and the numbers in the brackets refer to the front-to-rear dimension Or the heàt exchangers.
Other conditions are as rOllows:
Face velocity Or Heat Exchangers: 3 m/s Rate o~ Air Flow throu~h Heat Exchan~ers: 1200 m3/h Face area o~ Heat Exchan~ers: 0.11 m - 23 - , ~,~ ... . .
~L07~3!3Z~) 1 Effective Length of Heat Exchanging Tubes: 510 mm Diameter of Heat Exchanging Tubes: 95 mm Pitch of Fins of Heat Exchangers: 3 mm As the results of the experiments conducted under the aforesaid conditions, it has been ascertained that it is possible to prevent the formation of dew and frost when the heat and moisture transferring system according to the invention is permitted to operate under the aforesaid conditions, provided that the heat transmitting system 5 is designed such that the heat exchangers 18 and 19 each have the rows of the numbers set forth in the table.
Experiments were further conducted without using the heat exchangers 18 and 19 when the return air RA had a temperature 20C and a humidity 75%. When the outdoor air OA has a humidity 100% and a tempera-ture below 5C e.g. 0C for example, the straight line connecting the point of the return air RA of a tempera-ture 20C and a humidity 75% to the point of the outdoor air OA of a temperature 0C and a humidity 100~ was found to intersect the saturation line of relative humidity 100%. Thus the elimination of the heat exchangers 18 and 19 under the aforesaid conditions caused the formation of dew and frost to occur in the heat and moisture transferring device 3, thereby making it impossible to continue the operation of the heat and moisture transferring system.
From the foregoing description, it will be apparent that the heat and moisture transferring system according to the invention enables heat recovery to be ,. . . : ,. -: .
~ID7 !3~
effected with a high degree of efficiency without causing the formation of dew and/or frost in the heat and moisture trans-ferring device 3. Other embodiments of the invention will now be described with reference to Figs. 7, 10 and 11.
Fig. 7 shows another embodiment wherein the heat and moisture transferring device 3 comprises th~ known static heat and moisture transferrer matrix 4 shown in Fig. 2, and wherein the two heat exchangers 18 and 19 are formed as a unitary heat exchanger of a natural circulation type. The unitary heat exchanger comprises a plurality of heat exchanging tubes or heat pipes, each including a hollow straight tube having closed opposite ends and a multiplicity of fins pro-jecting from the outer periphery thereof, and filled with a suitable refrigerant. The heat pipes may be arranged ver-tically or aslant and located across the air supply passage 1 and air exhaust passage 2 disposed in parallel relationship.
The heat pipes are of a known type, in which refrigerant will be naturally circulated therein. More specifically, in each heat pipe, the refrigerant in a liquid state disposed in the lower portion thereof is vaporized into a gaseous state when heated by return aix RA of high tempera-ture and flows upwardly into the upper portion where the gaseous-refrigerant gives off heat-into the outdoor air OA
of low temperature and changes back into a liquid state.
The liquid refrigerant flows back to the original ~ ' ;~
:~713~
lower portion, thus completing a cycle of circulation. The heat pipes can also be used in case where the air supply passage 1 and air exhaust passage 2 are disposed horizontally.
In such a case, the heat pipes must be arrange~ horizontally.
In order to establish a natural circulation of the refrigerant in the heat pipes disposed horizontally, each heat pipe should be provided with a layer of porous material having a mul-titude of fine passages on its inner surface, so that the interior of each heat pipe is aivided into two regions, one providing passages for liquid refrigerant and the other providing passages for gas refrigerant. By this arrangement, smooth circulation of the refrigerant can be established in each heat pipe, even if the heat pipe is disposed horizontally.
The heat and moisture transferring device 3 is of the type which comprises the known static type heat and moisture transferrer matrix 4 shown and described with reference to Fig. 2. This type,of heat and moisture transferring device 3 is advantageous because it is simple in construction and requires no power source to operate the same.
The heat and moistuxe transferring system constructed as aformentioned offers the advantage of -requiring no power at all to operate the same. In addition, by arranging the heat transmitting system horizontally, it is possible to render the same opera-tive in the summertime as well as in the wintertime.
Particularly, this embodiment of the invention offers an advantage in that the formation of dew in excessive quantities in the heat and moisture transferrer matrix 4 ~ ~ .
- : . , ~ - - .. ., . .. . , , :
~788~
1 by outdoor air OA Or high temperature and high humldity can be prevented.
Fig. 10 shows still another embodiment wherein an on-off valve 24 is mounted in the closed circuit Or the heat transmitting system 5 in which a heat transmit-ting medium is circulated in gravity circulation accom-panied by a change in phase or in forced circulation.
When the system is not in use, the on-orf valve 24 is closed so as to completely stop the circulation of the heat-transmittlng medium. Thus the pro~ision of the on-off valve 24 prevents unnecessary operation of the system by stopping the circulation of the heat trans-mitting medium, thereby offering the advantage of increasing the heat recovery efficiency of khe heat and moisture transferring system.
Another feature of the embodiment shown ln ~ig. 10 is that a bypass damper 25 is mounted in a portion of the partition wall 11, separating the air supply passage 1 from the air exhaust passage 2. The bypass damper 25 normally forms a part of the partition wall 11, buk, when in operation, permits a portion of the precooled return air RA' to flow in bypass current from the air exhaust~
passage 2 to a portion of the air supply passage 1 which is disposed aownstream of the heat and moisture transferring device 3.
The provision of the bypass damper 25 offers the following advantages. In initial stages of the operation of the air conditioner in a heating mode, . 30 ~ ' ~, .
:'. , : ' , ' ' . ~ . :: .
~C~78~
1 the space is not heated satisfactorily and the tempera-ture of return air RA is so low that the temperature of the heat transmitting medium in the heat exchanger 18 is not sufficiently high to permit the heat and moisture transferrer matrix 4 to function satisfactorily. When this is the case~ the heat exchanger 18 is unable to satisfactorily preheat outdoor air OA Or low temperature.
When the aforesaid abnormal cond~tion exists, the bypass dampter 25, is actuated to allow a portion of the pre-cooled return air RA' to flow in bypass current and jointhe return air RA which effects heat exchange with the heat transmitting medium at the heat exchanger 19 can be increased in volume without materially increasing the volume of exhaust air EA, thereby making it possible to sufficiently raise the temper~ture of the heat trans-mitting medium. Thus the outdoor air OA can be suf-ficiently preheated by the heat exchanger^lB so that the formation of dew and frost in the heat and moisture trans-ferring device 3 can be prevented, even when the abnormal operating condition exists.
Fig. 11 shows still another embodiment in which the heat exchangers 18 and 19 are each divided into two sections or heat exchangers 18 and 19 which function as -heat exchangers of the lower temperature sidç and heat exchangers 18' and 19' which function as heat exchangers of the higher temperature side when the air conditioner operates in a heating mode. Hea~ exchanging tubes of ,~
, - ~8 -~ ' ' , .. .
1~7~38Z(3 1 the heat exchangers 18 and 19 are interconnected at upper ends thereof by a piping 20, and at lower ends thereof by a piping 21. Heat exchangin~ tubes of the heat exchangers 18' and 19' are interconnected at upper ends thereof by a piping 20l and at lower ends thereof by a piping 21'. Thus the heat transmltting system of this embodiment is formed as a double heat exchanging systems, so that the heat recovery efficiency can be increased as compared with the hea~ and moisture trans- -ferring system comprising a heat transmitting system formed as a single heat exchanging system.
The numerals 23, 23' and 24, 2l1' designate pressure delivery devices i.g. pumps or compressors and on-off valves mounted in the piping 21, 21' respectively.
When the heat and moisture transferring system according to the invention is used for effectin~ venti-lation of a freezing chamber, the system has effects if outdoor air OA has a relatively high temperature. In 2b this case, if the system is operated in a condition in which the return air RA, exhaust air EA, outdoor air OA and supply air SA of the embodiment shown in Fig. 6 are replaced by outdoor air OA, supply air SA, return air RA and exhaust air EA respectively, then it will be possible to cool the outdoor air of high temperature into cooled air for effecting ventilation.
From the foregoing descriptiong it will be appreciated that the heat and moisture transferring system according to the invention comprises, in combina-tion, an heat and mois~ure transferring device 3 which .
.
~7~3Z~
1 utilizes not only sensible heat but also latent heat, and a heat transmitting system 5 including a closed circuit interconnecting two heat exchangers. The heat exchangers are each designed to have a suitable heat exchanging capacity as shown in a psychrometric chart as aforesaid, so that the system permits heat to be removed ~rom return air from the heated space and to be imparted to fresh outdoor air supplied from the atmos-phere. In this way, ventilation of the cooled or heated space can be effected satisfactorily by utilizing the heat removed from the return air from the cooled or heated space. The provision of the two heat exchangers enables the heat and moisture transferring system to function with a high degree of efficiency without the formation of dew and frost even in the wintertime when cold is intense. Thus, the heat and moisture transferring system according to the invention is characterized by increased range of low temperatures in which it can have application.
Other conditions are as rOllows:
Face velocity Or Heat Exchangers: 3 m/s Rate o~ Air Flow throu~h Heat Exchan~ers: 1200 m3/h Face area o~ Heat Exchan~ers: 0.11 m - 23 - , ~,~ ... . .
~L07~3!3Z~) 1 Effective Length of Heat Exchanging Tubes: 510 mm Diameter of Heat Exchanging Tubes: 95 mm Pitch of Fins of Heat Exchangers: 3 mm As the results of the experiments conducted under the aforesaid conditions, it has been ascertained that it is possible to prevent the formation of dew and frost when the heat and moisture transferring system according to the invention is permitted to operate under the aforesaid conditions, provided that the heat transmitting system 5 is designed such that the heat exchangers 18 and 19 each have the rows of the numbers set forth in the table.
Experiments were further conducted without using the heat exchangers 18 and 19 when the return air RA had a temperature 20C and a humidity 75%. When the outdoor air OA has a humidity 100% and a tempera-ture below 5C e.g. 0C for example, the straight line connecting the point of the return air RA of a tempera-ture 20C and a humidity 75% to the point of the outdoor air OA of a temperature 0C and a humidity 100~ was found to intersect the saturation line of relative humidity 100%. Thus the elimination of the heat exchangers 18 and 19 under the aforesaid conditions caused the formation of dew and frost to occur in the heat and moisture transferring device 3, thereby making it impossible to continue the operation of the heat and moisture transferring system.
From the foregoing description, it will be apparent that the heat and moisture transferring system according to the invention enables heat recovery to be ,. . . : ,. -: .
~ID7 !3~
effected with a high degree of efficiency without causing the formation of dew and/or frost in the heat and moisture trans-ferring device 3. Other embodiments of the invention will now be described with reference to Figs. 7, 10 and 11.
Fig. 7 shows another embodiment wherein the heat and moisture transferring device 3 comprises th~ known static heat and moisture transferrer matrix 4 shown in Fig. 2, and wherein the two heat exchangers 18 and 19 are formed as a unitary heat exchanger of a natural circulation type. The unitary heat exchanger comprises a plurality of heat exchanging tubes or heat pipes, each including a hollow straight tube having closed opposite ends and a multiplicity of fins pro-jecting from the outer periphery thereof, and filled with a suitable refrigerant. The heat pipes may be arranged ver-tically or aslant and located across the air supply passage 1 and air exhaust passage 2 disposed in parallel relationship.
The heat pipes are of a known type, in which refrigerant will be naturally circulated therein. More specifically, in each heat pipe, the refrigerant in a liquid state disposed in the lower portion thereof is vaporized into a gaseous state when heated by return aix RA of high tempera-ture and flows upwardly into the upper portion where the gaseous-refrigerant gives off heat-into the outdoor air OA
of low temperature and changes back into a liquid state.
The liquid refrigerant flows back to the original ~ ' ;~
:~713~
lower portion, thus completing a cycle of circulation. The heat pipes can also be used in case where the air supply passage 1 and air exhaust passage 2 are disposed horizontally.
In such a case, the heat pipes must be arrange~ horizontally.
In order to establish a natural circulation of the refrigerant in the heat pipes disposed horizontally, each heat pipe should be provided with a layer of porous material having a mul-titude of fine passages on its inner surface, so that the interior of each heat pipe is aivided into two regions, one providing passages for liquid refrigerant and the other providing passages for gas refrigerant. By this arrangement, smooth circulation of the refrigerant can be established in each heat pipe, even if the heat pipe is disposed horizontally.
The heat and moisture transferring device 3 is of the type which comprises the known static type heat and moisture transferrer matrix 4 shown and described with reference to Fig. 2. This type,of heat and moisture transferring device 3 is advantageous because it is simple in construction and requires no power source to operate the same.
The heat and moistuxe transferring system constructed as aformentioned offers the advantage of -requiring no power at all to operate the same. In addition, by arranging the heat transmitting system horizontally, it is possible to render the same opera-tive in the summertime as well as in the wintertime.
Particularly, this embodiment of the invention offers an advantage in that the formation of dew in excessive quantities in the heat and moisture transferrer matrix 4 ~ ~ .
- : . , ~ - - .. ., . .. . , , :
~788~
1 by outdoor air OA Or high temperature and high humldity can be prevented.
Fig. 10 shows still another embodiment wherein an on-off valve 24 is mounted in the closed circuit Or the heat transmitting system 5 in which a heat transmit-ting medium is circulated in gravity circulation accom-panied by a change in phase or in forced circulation.
When the system is not in use, the on-orf valve 24 is closed so as to completely stop the circulation of the heat-transmittlng medium. Thus the pro~ision of the on-off valve 24 prevents unnecessary operation of the system by stopping the circulation of the heat trans-mitting medium, thereby offering the advantage of increasing the heat recovery efficiency of khe heat and moisture transferring system.
Another feature of the embodiment shown ln ~ig. 10 is that a bypass damper 25 is mounted in a portion of the partition wall 11, separating the air supply passage 1 from the air exhaust passage 2. The bypass damper 25 normally forms a part of the partition wall 11, buk, when in operation, permits a portion of the precooled return air RA' to flow in bypass current from the air exhaust~
passage 2 to a portion of the air supply passage 1 which is disposed aownstream of the heat and moisture transferring device 3.
The provision of the bypass damper 25 offers the following advantages. In initial stages of the operation of the air conditioner in a heating mode, . 30 ~ ' ~, .
:'. , : ' , ' ' . ~ . :: .
~C~78~
1 the space is not heated satisfactorily and the tempera-ture of return air RA is so low that the temperature of the heat transmitting medium in the heat exchanger 18 is not sufficiently high to permit the heat and moisture transferrer matrix 4 to function satisfactorily. When this is the case~ the heat exchanger 18 is unable to satisfactorily preheat outdoor air OA Or low temperature.
When the aforesaid abnormal cond~tion exists, the bypass dampter 25, is actuated to allow a portion of the pre-cooled return air RA' to flow in bypass current and jointhe return air RA which effects heat exchange with the heat transmitting medium at the heat exchanger 19 can be increased in volume without materially increasing the volume of exhaust air EA, thereby making it possible to sufficiently raise the temper~ture of the heat trans-mitting medium. Thus the outdoor air OA can be suf-ficiently preheated by the heat exchanger^lB so that the formation of dew and frost in the heat and moisture trans-ferring device 3 can be prevented, even when the abnormal operating condition exists.
Fig. 11 shows still another embodiment in which the heat exchangers 18 and 19 are each divided into two sections or heat exchangers 18 and 19 which function as -heat exchangers of the lower temperature sidç and heat exchangers 18' and 19' which function as heat exchangers of the higher temperature side when the air conditioner operates in a heating mode. Hea~ exchanging tubes of ,~
, - ~8 -~ ' ' , .. .
1~7~38Z(3 1 the heat exchangers 18 and 19 are interconnected at upper ends thereof by a piping 20, and at lower ends thereof by a piping 21. Heat exchangin~ tubes of the heat exchangers 18' and 19' are interconnected at upper ends thereof by a piping 20l and at lower ends thereof by a piping 21'. Thus the heat transmltting system of this embodiment is formed as a double heat exchanging systems, so that the heat recovery efficiency can be increased as compared with the hea~ and moisture trans- -ferring system comprising a heat transmitting system formed as a single heat exchanging system.
The numerals 23, 23' and 24, 2l1' designate pressure delivery devices i.g. pumps or compressors and on-off valves mounted in the piping 21, 21' respectively.
When the heat and moisture transferring system according to the invention is used for effectin~ venti-lation of a freezing chamber, the system has effects if outdoor air OA has a relatively high temperature. In 2b this case, if the system is operated in a condition in which the return air RA, exhaust air EA, outdoor air OA and supply air SA of the embodiment shown in Fig. 6 are replaced by outdoor air OA, supply air SA, return air RA and exhaust air EA respectively, then it will be possible to cool the outdoor air of high temperature into cooled air for effecting ventilation.
From the foregoing descriptiong it will be appreciated that the heat and moisture transferring system according to the invention comprises, in combina-tion, an heat and mois~ure transferring device 3 which .
.
~7~3Z~
1 utilizes not only sensible heat but also latent heat, and a heat transmitting system 5 including a closed circuit interconnecting two heat exchangers. The heat exchangers are each designed to have a suitable heat exchanging capacity as shown in a psychrometric chart as aforesaid, so that the system permits heat to be removed ~rom return air from the heated space and to be imparted to fresh outdoor air supplied from the atmos-phere. In this way, ventilation of the cooled or heated space can be effected satisfactorily by utilizing the heat removed from the return air from the cooled or heated space. The provision of the two heat exchangers enables the heat and moisture transferring system to function with a high degree of efficiency without the formation of dew and frost even in the wintertime when cold is intense. Thus, the heat and moisture transferring system according to the invention is characterized by increased range of low temperatures in which it can have application.
Claims (20)
PROPERTY OR PRIVILEGE IS CLAIMED ARE DEFINED AS FOLLOWS:
1. A system for transferring heat and moisture between first and second air streams comprising, in combination:
a first conduit means for said first air stream;
a second conduit means for said second air stream;
heat and moisture transferring means comprising a multitude of open-ended air passages defined by moisture absorptive and heat conductive material, a first set of said air passages being disposed in said first conduit means for permitting said first air stream to pass therethrough and a second set of said air passages being disposed in said second conduit means for permitting said second air stream to pass therethrough;
means disposing the first and second set of air passages alternatively so that heat and moisture are transferred between the first and second air streams passing through said passages through the moisture absorptive and heat conductive material; and a heat transmitting system including a first heat exchanging means disposed in said first conduit means up-stream of said heat and moisture transferring means for exchanging heat between said first air stream and a heat transmitting medium, a second heat exchanging means disposed in said second conduit means upstream of said heat and moisture transferring means for exchanging heat between said second air stream and said heat transmitting medium, and third conduit means connecting said first and second heat exchanging means together for forming a closed circuit for said heat transmitting medium.
a first conduit means for said first air stream;
a second conduit means for said second air stream;
heat and moisture transferring means comprising a multitude of open-ended air passages defined by moisture absorptive and heat conductive material, a first set of said air passages being disposed in said first conduit means for permitting said first air stream to pass therethrough and a second set of said air passages being disposed in said second conduit means for permitting said second air stream to pass therethrough;
means disposing the first and second set of air passages alternatively so that heat and moisture are transferred between the first and second air streams passing through said passages through the moisture absorptive and heat conductive material; and a heat transmitting system including a first heat exchanging means disposed in said first conduit means up-stream of said heat and moisture transferring means for exchanging heat between said first air stream and a heat transmitting medium, a second heat exchanging means disposed in said second conduit means upstream of said heat and moisture transferring means for exchanging heat between said second air stream and said heat transmitting medium, and third conduit means connecting said first and second heat exchanging means together for forming a closed circuit for said heat transmitting medium.
2. A system as set forth in claim 1, further comprising an additional heat transmitting system including a third heat exchanging means disposed in said first conduit means upstream of said first heat exchanging means for exchanging heat between said first air stream and heat transmitting medium, a fourth heat exchanging means disposed in said second conduit means between said second heat exchanging means and said heat and moisture transferring means for exchanging heat between said second air stream and said heat transmitting medium, and fourth conduit means forming a closed circuit for said heat transmitting medium including said third and fourth heat exchanging means.
3. A system as set forth in claim 1, wherein said heat transmitting medium circulated in said heat trans-mitting system is a non-evaporative liquid, and said heat transmitting system includes means for forcedly circulating said liquid.
4. A system as set forth in claim 1, wherein said heat transmitting medium is a condensable gas capable of transferring heat by changing its phase.
5. A system as set forth in claim 4, wherein said heat transmitting system comprises a plurality of heat pipes, one portion of each of said heat pipes extending into said first air conduit means to function as said first heat exchanging means, another portion of each of said heat pipes extending into said second air conduit means to function as said second heat exchanging means, and still another portion of each of said heat pipes interposed between said one portion and said another portion functioning as said third conduit means.
6. A system as set forth in claim 4, wherein one of said two heat exchanging means brought into contact with one of said air streams of higher temperature is located at a lower level than the other heat exchanging means brought into contact with the other of said air streams of lower temperature, whereby said condensable gas can be circulated in gravity circulation.
7. A system as set forth in claim 4, wherein said heat transmitting system includes means for forcedly circulating said condensable gas.
8. A system as set forth in claim 4, wherein said heat transmitting system includes an on-off valve, whereby said condensable gas is circulated only when it is necessary to do so.
9. A system as set forth in claim 6, wherein said heat transmitting system includes an on-off valve, whereby said condensable gas is circulated only when it is necessary to do so.
10. A system as set forth in claim 1, further comprising means for permitting a portion of said second air stream to flow in bypass current from between said heat and moisture transferring means and said second heat exchanging means into said first air stream downstream of said heat and moisture transferring means.
11. A system as set forth in claim 1, wherein said first air stream is outdoor air of low temperature and said second air stream is return air returned from a heated space and wherein said heat transmitting system is designed in such a manner that said first heat exchang-ing means is operative to preheat said outdoor air to a predetermined first condition (OA'), said second heat exchanging means is operative to precool said return air to a predetermined second condition (RA'), and the straight line connecting the points representing said first condition (OA') and said second condition (RA') in a psychrometric chart is disposed inwardly of the saturation line.
12. A system as set forth in claim 11, further comprising an additional heat transmitting system including a third heat exchanging means disposed in said first conduit means upstream of said first heat exchanging means for exchanging heat between said first air stream and heat transmitting medium, a fourth heat exchanging means disposed in said second conduit means between said second heat exchanging means and said heat and moisture transferring means for exchanging heat between said second air stream and said heat trans-mitting medium, and fourth conduit means forming a closed circuit for said heat transmitting medium including said third and fourth heat exchanging means.
13. A system as set forth in claim 11, wherein said heat transmitting medium circulated in said heat transmitting system is a non-evaporative liquid, and said heat transmitting system includes means for forcedly circulating said liquid.
14. A system as set forth in claim 11, wherein said heat transmitting medium is a condensable gas capable of transferring heat by changing its phase.
15. A system as set forth in claim 14, wherein said heat transmitting system comprises a plurality of heat pipes, one portion of each of said heat pipes extending into said first air conduit means to function as said first heat exchanging means, another portion of each of said heat pipes extending into said second conduit means to function as said second heat exchanging means, and still another portion of each of said heat pipes interposed between said one portion and said another portion functioning as said third conduit means.
16. A system as set forth in claim 14, wherein said second heat exchanging means brought into contact with the return air of higher temperature is located at a lower level than said first heat exchanging means brought into contact with the outdoor air of lower temperature, whereby said condensable gas can be circulated in gravity circulation.
17. A system as set forth in claim 14, wherein said heat transmitting system includes means for forcedly circulating said condensable gas.
18. A system as set forth in claim 14, wherein said heat transmitting system includes an on-off valve, whereby said condensable gas is circulated only when it is necessary to do so.
19. A system as set forth in claim 16, wherein said heat transmitting system includes an on-off valve, whereby said condensable gas is circulated only when it is necessary to do so.
20. A system as set forth in claim 11, further comprising means for permitting a portion of said second air stream to flow in bypass current from between said heat and moisture transferring means and said second heat exchanging means into said first air stream downstream of said heat and moisture transferring means.
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP51081672A JPS5818566B2 (en) | 1976-07-08 | 1976-07-08 | heat recovery equipment |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA1078820A true CA1078820A (en) | 1980-06-03 |
Family
ID=13752824
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA282,233A Expired CA1078820A (en) | 1976-07-08 | 1977-07-07 | Heat and moisture transferring system |
Country Status (7)
| Country | Link |
|---|---|
| JP (1) | JPS5818566B2 (en) |
| CA (1) | CA1078820A (en) |
| DE (1) | DE2729862C3 (en) |
| FR (1) | FR2357828A1 (en) |
| GB (1) | GB1551647A (en) |
| SE (1) | SE431908B (en) |
| SU (1) | SU976862A3 (en) |
Families Citing this family (31)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5488639A (en) * | 1977-12-23 | 1979-07-13 | Toyo Seisakusho Kk | Precooling and preheating device |
| DE3018046A1 (en) * | 1979-05-12 | 1980-11-20 | Mckirdy | TEMPERATURE CONTROL SYSTEM |
| DE3100915C2 (en) * | 1980-05-26 | 1986-08-07 | Sharp K.K., Osaka | Air conditioning unit for recirculation mode |
| JPS57165063A (en) * | 1981-04-07 | 1982-10-09 | Nissan Motor Co Ltd | Air-conditioner for coating |
| EP0097216A1 (en) * | 1982-06-22 | 1984-01-04 | Grandi Lavori Strutture Spa | Thermal economizer for domestic heating installations |
| DE3502444A1 (en) * | 1985-01-25 | 1986-07-31 | Lüftungs-, Klima-, Schalldämpfanlagen Lyttek GmbH, 4235 Schermbeck | Device for removing outgoing air and supplying incoming air |
| SE8500584L (en) * | 1985-02-08 | 1986-08-09 | Munters Ab Carl | SET AND DEVICE FOR CONDITIONING GAS |
| DE3718196A1 (en) * | 1987-05-29 | 1988-12-15 | Kraftanlagen Ag | METHOD AND DEVICE FOR THE REMOVAL OF IZING FROM CIRCULATING REGENERATIVE HEAT AND / OR FABRIC EXCHANGERS |
| NO179227C (en) * | 1994-05-24 | 1996-08-28 | Martinsen As Finn | Frost protection device for heat recoverers |
| CA2134168C (en) * | 1994-10-24 | 2002-06-11 | Frederic Lagace | Ventilation system |
| US5826641A (en) * | 1994-10-27 | 1998-10-27 | Aaon, Inc. | Air conditioner with heat wheel |
| GB2296968A (en) * | 1994-12-02 | 1996-07-17 | Thermal Technology | Heat exchange ventilator |
| FI100132B (en) * | 1995-03-03 | 1997-09-30 | Abb Installaatiot Oy | Arrangement in connection with an air handling unit |
| DE19512852C1 (en) * | 1995-04-06 | 1996-05-23 | S & E Klima Sondertechnik Gmbh | Air conditioning using evaporative cooling |
| MY117922A (en) * | 1996-12-27 | 2004-08-30 | Ebara Corp | Air conditioning system |
| CN1123738C (en) * | 1997-03-25 | 2003-10-08 | 株式会社荏原制作所 | Air conditioning system |
| JPH11141917A (en) | 1997-11-12 | 1999-05-28 | Daikin Ind Ltd | Dehumidifying/humidifying air supply apparatus |
| US6083300A (en) * | 1998-08-25 | 2000-07-04 | Gas Research Institute | Dual mode air treatment apparatus and method |
| FI982667A (en) * | 1998-12-09 | 2000-06-10 | Abb Installaatiot Oy | Method and apparatus for recovery of heat and moisture |
| JP2001041494A (en) * | 1999-07-26 | 2001-02-13 | Ebara Corp | Heat pump |
| NO996098A (en) * | 1999-12-09 | 2000-10-02 | Ove T Njaa | Device for air conditioning with heat recovery |
| US6575228B1 (en) * | 2000-03-06 | 2003-06-10 | Mississippi State Research And Technology Corporation | Ventilating dehumidifying system |
| DE10215587B4 (en) * | 2002-04-10 | 2006-03-23 | Stiebel Eltron Gmbh & Co. Kg | Device for freezing a heat exchanger apparatus |
| US6751964B2 (en) | 2002-06-28 | 2004-06-22 | John C. Fischer | Desiccant-based dehumidification system and method |
| KR100601212B1 (en) | 2004-12-09 | 2006-07-13 | 주식회사 대우일렉트로닉스 | Heat Recovery Ventilator Installed a Heat-Pipe |
| TWI295358B (en) * | 2004-12-28 | 2008-04-01 | Foxconn Tech Co Ltd | Rotary total heat exchange apparatus |
| DE102006007845B4 (en) | 2006-02-17 | 2014-08-21 | Menerga Gmbh | Plant for heating a hall such as a swimming pool |
| US7886986B2 (en) | 2006-11-08 | 2011-02-15 | Semco Inc. | Building, ventilation system, and recovery device control |
| JP4866222B2 (en) * | 2006-12-07 | 2012-02-01 | 大阪瓦斯株式会社 | Air conditioner |
| JP5219624B2 (en) * | 2008-05-26 | 2013-06-26 | 三菱電機株式会社 | Heat recovery equipment |
| JP2022187736A (en) * | 2021-06-08 | 2022-12-20 | パナソニックＩｐマネジメント株式会社 | Humidity control device |
Family Cites Families (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR1122032A (en) * | 1954-02-03 | 1956-08-30 | combined heat and humidity exchanger | |
| DE1108371B (en) * | 1958-02-21 | 1961-06-08 | Schmidt Sche Heissdampf | Regenerative air or gas preheater, the heat storage masses of which are arranged parallel to one another and can be moved across channels |
| US3640090A (en) * | 1970-06-03 | 1972-02-08 | American Standard Inc | Cold-heat recovery for air conditioning |
| JPS524590Y2 (en) * | 1972-07-10 | 1977-01-31 | ||
| JPS49100834A (en) * | 1973-01-30 | 1974-09-24 | ||
| JPS50106032U (en) * | 1974-02-06 | 1975-09-01 | ||
| JPS5616879B2 (en) * | 1974-02-14 | 1981-04-18 | ||
| FR2299605A1 (en) * | 1975-01-31 | 1976-08-27 | Bernier Jean Paul | Contraflow heat exchange system - has several heat pumps with heat exchangers adjacent and connected together in series |
-
1976
- 1976-07-08 JP JP51081672A patent/JPS5818566B2/en not_active Expired
-
1977
- 1977-06-29 GB GB27232/77A patent/GB1551647A/en not_active Expired
- 1977-07-01 DE DE2729862A patent/DE2729862C3/en not_active Expired
- 1977-07-07 FR FR7720988A patent/FR2357828A1/en active Granted
- 1977-07-07 CA CA282,233A patent/CA1078820A/en not_active Expired
- 1977-07-07 SE SE7707930A patent/SE431908B/en not_active IP Right Cessation
- 1977-07-08 SU SU772503759A patent/SU976862A3/en active
Also Published As
| Publication number | Publication date |
|---|---|
| FR2357828A1 (en) | 1978-02-03 |
| JPS536951A (en) | 1978-01-21 |
| SU976862A3 (en) | 1982-11-23 |
| DE2729862C3 (en) | 1980-10-16 |
| DE2729862B2 (en) | 1980-02-21 |
| JPS5818566B2 (en) | 1983-04-13 |
| DE2729862A1 (en) | 1978-01-12 |
| GB1551647A (en) | 1979-08-30 |
| FR2357828B1 (en) | 1982-04-23 |
| SE7707930L (en) | 1978-01-09 |
| SE431908B (en) | 1984-03-05 |
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Legal Events
| Date | Code | Title | Description |
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| MKEX | Expiry |