CN102705920B - Double-cold-source heat pump total heat recovery humidity regulating and temperature controlling fresh air unit and control method thereof - Google Patents

Double-cold-source heat pump total heat recovery humidity regulating and temperature controlling fresh air unit and control method thereof Download PDF

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Publication number
CN102705920B
CN102705920B CN201210163979.5A CN201210163979A CN102705920B CN 102705920 B CN102705920 B CN 102705920B CN 201210163979 A CN201210163979 A CN 201210163979A CN 102705920 B CN102705920 B CN 102705920B
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air
new wind
heat pump
indoor
compressor
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CN201210163979.5A
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CN102705920A (en
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贺建鑫
潘京平
吕智
刘湘辉
刘波
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吕智
深圳市建筑设计研究总院有限公司
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    • YGENERAL 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
    • Y02TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02BCLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B30/00Energy efficient heating, ventilation or air conditioning [HVAC]
    • Y02B30/52Heat recovery pumps, i.e. heat pump based systems or units able to transfer the thermal energy from one area of the premises or part of the facilities to a different one, improving the overall efficiency
    • Y02B30/563

Abstract

The invention discloses a double-cold-source heat pump total heat recovery humidity regulating and temperature controlling fresh air unit and a control method thereof, and belongs to the fields of energy utilization technology and air conditioning. The fresh air unit comprises an air exhaust part, a fresh air treatment part, a surface heat exchanger and a heat pump system, wherein the heat pump system comprises a compressor, a condenser, a condensation heat recoverer, an evaporator and a throttling component. The fresh air unit utilizes indoor low-temperature and low-humidity exhausted air to exhaust condensation heat of a refrigeration system in summer, and utilizes indoor high-temperature and high-humidity exhausted air to exhaust evaporation cold energy of the refrigeration system in winter. The surface heat exchanger aims at performing pre-cooling and pre-dehumidification to high-temperature and high-humidity fresh air through chilled water dew point temperature. The heat pump system provides required cold energy and heat as well as the lower dew point temperature that the chilled water is unaccessible to for the fresh air treatment part.

Description

Double-cold source heat pump total heat recovery damping temperature control Fresh air handling units and control mode thereof

Technical field

The present invention relates to a kind of heat pump full heat recovery fresh air process unit, particularly double-cold source heat pump total heat recovery damping temperature control Fresh air handling units and control mode thereof..

Background technology

China's air conditioning in residential buildings system mostly adopts new return air mixed mode, and because most of air is in indoor circulation, what it is such that pollutant can not be very fast is discharged to outdoor, and harm humans is healthy.Strengthen resh air requirement (or adopting the method for operation of all-fresh air), the harmful substance of indoor can be diluted and discharge outdoor, significantly improve indoor air quality.But then, the increase of resh air requirement makes Fresh air handing energy consumption greatly increase.In addition to the processing mode dehumidification mode adopting chilled water or directly evaporation at present of air, there is the drawback of the following aspects in this air conditioning mode: one, the condensation temperature of air cooling refrigeration machine is higher, and Energy Efficiency Ratio is low more; Two, the chilled water temperature that provides of central cooling-water machine certain (namely dew-point temperature is certain), is difficult to process and arrives humiture autonomous system to the requirement of new wind water capacity; Three, the change adapting to heat moisture ratio is difficult to.Only being cooled air by evaporation mode and dehumidify, its sensible heat absorbed is with latent heat than can only changing in certain scope, and the heat moisture ratio of building actual needs changes in the larger context.Be generally the control of sacrificing relative humidity, compromised by the requirement only meeting indoor temperature, cause the phenomenon that indoor relative humidity is too high or too low; Four, cause the existence of condensed water because leaving air temp is too low, the surface of coil pipe defines the hotbed growing various mould, is degrading indoor air quality, causes multiple Cure of Sick Building Syndrome.Thus humiture is independently located erection system and is obtained and utilize more and more widely in recent years.

This double-cold source heat pump total heat recovery damping temperature control Fresh air handling units and control mode thereof., except being applied to general central air-conditioning cooling-water machine and ice-storage system, and be more suitable for in humiture autonomous system, so-called humiture independence control air conditioner system, temperature and humidity two is adopted to overlap independently air-conditioner control system, temperature respectively in control, conditioning chamber and humidity, thus the loss avoiding that in conventional air conditioning system, hot wet Combined Treatment is brought.Because temperature, humidity adopt independently control system, the requirement that not chummery heat moisture ratio constantly changes can be met, overcome in conventional air conditioning system the requirement being difficult to simultaneously meet epidemic disaster parameter, avoid the phenomenon of indoor humidity too high (or too low).

Which utilizes the combination of central air-conditioning freezing water and heat pump full heat recovery fresh air unit, the dew-point temperature avoiding the new wind of conventional central air-conditioning process is subject to the impact of chilled water temperature, does not reach the requirement of humiture autonomous system to new wind water capacity; Its basic function is: the system of process sensible heat and latent heat can while conditioning chamber in temperature and humidity.The ultra-low dew point temperature being controlled room air by the surface-type heat exchanger of chilled water and the direct-evaporation-type evaporimeter of heat pump processes latent heat and part sensible heat, heated up by condensation heat recoverer again, utilize heat pump condensation heat to heat up and reduce the relative humidity of new wind air-out, thus there is not the danger of the too low condensation of leaving air temp.Fresh air handing unit is also born simultaneously and is removed indoor CO2, peculiar smell, to ensure the task of IAQ.

In humiture independence control air conditioner system, need the new wind in outdoor that Fresh air handing unit provides dry, meeting hydrofuge, arrange CO2, arrange taste and the demand of fresh air is provided.Adopting conventional rotor dehumidification mode, is a kind of possible solution route, is namely attached to the wheel surface of aglite making with the hygroscopic material such as silica gel, molecular sieve.But the essence that rotary dehumidifier utilization efficiency of heat energy is low is dehumidifying is all constant-enthalpy process and non-isothermal process with these two processes of regeneration, psychrometric difference between wheel surface and air and temperature difference are all very uneven, cause very large irreversible loss, also there is the situation of new wind and air draft cross pollution simultaneously.Another dehumidification mode is that air first carries out pre-dehumidified through the surface-type heat exchanger of chilled water, and then refrigerant evaporator that is direct and low temperature carries out heat exchange (by lower dew-point temperature), steam in air is by the intensification condensed into through auxiliary condenser after condensed water, thus realize the superpower dehumidifying object of air, thus realize the moisture absorption process close to isothermal; Low temperature and low humidity air draft simultaneously contributes to reducing condensation temperature through condenser, thus substantially increases the Energy Efficiency Ratio of unit.Surface-type heat exchanger is adopted to be beyond one's reach low dew point evaporating temperature in conjunction with heat-pump dehumidification technical finesse air conditioner fresh air, particularly chilled water; New air draft is two autonomous channels, tunnel, has stopped cross pollution, has improved indoor air quality; The energy of system recoveries indoor exhaust wind, reduces Fresh air handing energy consumption; Improve heat pump Energy Efficiency Ratio, low taste thermal source is utilized, because heat pump can obtain the heat more than drive energy, contribute to environmental situation that is energy-conservation and that improve because coal-fired, fuel oil cause.

Summary of the invention

Object of the present invention aim to provide a kind of simple and reasonable, operate steadily, energy consumption is low double-cold source heat pump total heat recovery damping temperature control Fresh air handling units and control mode thereof, to overcome and to improve weak point of the prior art.

Design by this object double-cold source heat pump total heat recovery damping temperature control Fresh air handling units, be made up of air exhaust part, Fresh air handing part, surface-type heat exchanger and heat pump.In figure, solid line represents refrigeration working medium flow duct, and dotted line represents new wind and Air exhaust passage.

Described double-cold source heat pump total heat recovery damping temperature control Fresh air handling units, it is characterized in that the c interface of described four-way change-over valve is connected with one end of condenser, a interface is connected with the exhaust outlet of compressor, and b interface is connected with the air entry of compressor, and d interface is connected with one end of evaporimeter; The other end of condenser is connected with the other end of evaporimeter by throttle part.

Also be connected with magnetic valve a between described condenser and throttle part, magnetic valve a two ends are parallel with condensation heat recoverer, and wherein, one end that magnetic valve a is connected with condenser is connected with condensation heat recoverer with by magnetic valve b; Condensation heat recoverer is arranged on new wind air outlet place.

Described surface-type heat exchanger is arranged on new wind air inlet.

Described Fresh air handing part is containing new blower fan and humidifier, and humidifier is arranged between evaporimeter and condensation heat recoverer.

When outdoor air is hot humid air, open compressor, a, c orifice of cross valve reversal valve, b, d orifice, outdoor new wind, successively through the surface-type heat exchanger that chilled water runs, carries out pre-dehumidified; Lower the temperature further and degree of depth dehumidifying through evaporator again, then send into indoor after condensation heat recoverer heats up.The object of surface-type heat exchanger utilizes chilled water dew-point temperature to carry out precooling and pre-dehumidified to hot and humid new wind; The object of evaporimeter reaches chilled water by refrigerant evaporation to be beyond one's reach lower dew-point temperature, and removing surface-type heat exchanger cannot process the moisture in new wind further; Heating up through condensation heat recoverer makes its relative humidity reduce, to reach required air-out humiture again.The air draft of indoor low temperature low humidity, outside condenser discharge chamber, contributes to cooler condenser to strengthen its heat-sinking capability, and reduces power consumption raising Energy Efficiency Ratio.When outdoor air is low temperature dry air, open compressor, a, d orifice of cross valve reversal valve, b, c orifice, realized the mutual conversion of evaporimeter and condenser by cross valve commutation.The new wind of open-air seasoning, low temperature is successively after the surface-type heat exchanger preheating that superheated water runs, then through condenser and humidifier, by the humidification that heats up further, new wind is sent into indoor after warming and humidifying; The heat exhaust of condenser is used for promoting new wind leaving air temp further; The surface-type heat exchanger that hot water runs contributes to the stable operation of heat pump simultaneously to the preheating of new wind.Indoor hot and humid air, through evaporator, is discharged outdoor after cooling; Magnetic valve a opens, and magnetic valve b closes, and condensation heat recoverer does not work.

Summer and autumn season, when outdoor air humiture is applicable to, under central air-conditioning cooling-water machine ruuning situation, preferential compressor of closing heat pump, the surface-type heat exchanger that new wind is run by chilled water overcomes new wind load; In central air-conditioning cooling-water machine shutdown situation, new wind overcomes new wind and indoor load by the operation of heat pump, when indoor temperature and humidity is too low, close the compressor of heat pump, the air indoor outside discharge chamber and the air entering indoor outdoor carry out ventilation;

Change according to the season in Winter-Spring, when outside air temperature is applicable to, under central water-heating machine ruuning situation, and preferential compressor of closing heat pump, the surface-type heat exchanger that new wind is run by hot water overcomes new wind load; In central water-heating machine shutdown situation; new wind overcomes new wind and indoor load by the operation of heat pump; when indoor temperature and humidity is too high, close the compressor of heat pump, the air indoor outside discharge chamber and the air entering indoor outdoor carry out ventilation.

Described condensation heat recoverer and condenser are connected in series, and for reclaiming the condensation heat of refrigeration system, raising new wind leaving air temp and reducing relative humidity; If new wind leaving air temp is too low, magnetic valve b need be opened, magnetic valve a closes; If new wind leaving air temp is too high, then need magnetic valve a to open, magnetic valve b closes, and condensation heat recoverer does not work.

Present invention utilizes central air-conditioning freezing water and adopt heat pump techniques to connect incompatible process air conditioner fresh air, also by add in new wind part filtration and sterilizing unit can remove the dust and bacterium carried secretly in air, play the effect purified air, improve indoor air quality; System can reclaim the energy of indoor exhaust wind, reduces Fresh air handing energy consumption; Utilize heat pump to provide dehumidifying heat, low taste thermal source is utilized, because heat pump can obtain the heat more than drive energy, contribute to environmental situation that is energy-conservation and that improve because coal-fired, fuel oil cause.

Accompanying drawing explanation

Fig. 1 is one embodiment of the invention operation principle schematic diagram-summer operation schematic diagram.

Fig. 2 is another embodiment of the present invention operation principle schematic diagram-winter operation schematic diagram.

Detailed description of the invention

Below in conjunction with drawings and Examples, the invention will be further described.

See Fig. 1, this double-cold source heat pump total heat recovery damping temperature control Fresh air handling units, be made up of air exhaust part, Fresh air handing part, surface-type heat exchanger and heat pump.Heat pump comprises compressor 1, cross valve reversal valve 10, condenser 2, evaporimeter 4, condensation heat recoverer 5 and throttle part 9, and condensation heat recoverer 5 is arranged on new wind air outlet place; Air exhaust part is performed by exhaust blower 3; Surface-type heat exchanger is arranged on new wind air inlet; Fresh air handing part forms containing new blower fan 6 and humidifier 12.

The c interface of four-way change-over valve 10 is connected with one end of condenser 2, and a interface is connected with the exhaust outlet of compressor 1, and b interface is connected with the air entry of compressor 1, and d interface is connected with one end of evaporimeter 4; The other end of condenser 2 is connected with the other end of evaporimeter 4 by throttle part 9.

Also be connected with magnetic valve a8 between condenser 2 and throttle part 9, magnetic valve a8 two ends are parallel with condensation heat recoverer 5, and wherein, one end that magnetic valve a8 is connected with condenser 2 is connected with condensation heat recoverer 5 with by magnetic valve b7; Condensation heat recoverer 5 is arranged on new wind air outlet place.

The new blower fan 6 of Fresh air handing part is arranged on new wind air outlet place, and humidifier 12 is arranged between evaporimeter 4 and condensation heat recoverer 5.

The exhaust blower 3 air draft air outlet disposed in the interior place of air exhaust part, discharges condenser heat.

Surface-type heat exchanger 11 is arranged on new wind air inlet, carries out precooling to new wind.

Below the present invention is described in detail, in sum, is only one of the present invention preferred embodiment, when can not the scope of the present invention be limited, namely allly do impartial change according to the application's scope and modify, all should still belong in covering scope of the present invention.

its operation principle is:

One, summer operation

See Fig. 1, when outdoor air is hot humid air, open compressor 1, a, c orifice of cross valve reversal valve 10, b, d orifice, the new wind in outdoor of hot humid, successively through the surface-type heat exchanger 11 that chilled water runs, carries out pre-dehumidified; Again through evaporator 4 cooling and degree of depth dehumidifying further, then send into indoor after condensation heat recoverer 5 heats up.The object of evaporimeter 4 reaches chilled water by refrigerant evaporation to be beyond one's reach lower dew-point temperature, and removing surface-type heat exchanger cannot process the moisture in new wind further; Heating up through condensation heat recoverer 5 makes its relative humidity reduce, to reach required air-out humiture again.The air draft of indoor low temperature low humidity, outside condenser 2 discharge chamber, contributes to cooler condenser to strengthen its heat-sinking capability, and reduces power consumption raising Energy Efficiency Ratio.If new wind leaving air temp is too low, magnetic valve b7 need be opened, magnetic valve a8 closes, and the condensation heat of condensation heat recoverer 5 is for raising new wind leaving air temp and reducing relative humidity; If new wind leaving air temp is too high, then need magnetic valve a8 to open, magnetic valve b7 closes, and condensation heat recoverer 5 does not work.

Two, winter operation

See Fig. 2, when outdoor air is low temperature dry air, open compressor 1, a, d orifice of cross valve reversal valve 10, b, c orifice, realized the mutual conversion of evaporimeter and condenser by cross valve commutation.The new wind of open-air seasoning, low temperature is successively after surface-type heat exchanger 11 preheating that superheated water runs, then through condenser 4 and humidifier 12, by the humidification that heats up further, new wind is sent into indoor after warming and humidifying; The heat exhaust of condenser 4 is used for promoting new wind leaving air temp further; The surface-type heat exchanger 11 that hot water runs contributes to the stable operation of heat pump simultaneously to the preheating of new wind.Indoor hot and humid air, through evaporator 2, is discharged outdoor after cooling; Magnetic valve a8 opens, and magnetic valve b7 closes, and condensation heat recoverer 5 does not work.

Three, transition season Fresh air handling units runs explanation

Summer and autumn season, when outdoor air humiture is applicable to, under central air-conditioning cooling-water machine ruuning situation, preferential compressor 1 of closing heat pump, the surface-type heat exchanger 11 that new wind is run by chilled water overcomes new wind load; In central air-conditioning cooling-water machine shutdown situation, new wind overcomes new wind and indoor load by the operation of heat pump, when indoor temperature and humidity is too low, close the compressor 1 of heat pump, the air indoor outside discharge chamber and the air entering indoor outdoor carry out ventilation;

Change according to the season in Winter-Spring, when outside air temperature is applicable to, under central water-heating machine ruuning situation, and preferential compressor 1 of closing heat pump, the surface-type heat exchanger 11 that new wind is run by hot water overcomes new wind load; In central water-heating machine shutdown situation; new wind overcomes new wind and indoor load by the operation of heat pump; when indoor temperature and humidity is too high, close the compressor 1 of heat pump, the air indoor outside discharge chamber and the air entering indoor outdoor carry out ventilation.

Claims (1)

1. double-cold source heat pump total heat recovery damping temperature control Fresh air handling units, it is characterized in that, be made up of air exhaust part, Fresh air handing part, surface-type heat exchanger and heat pump, described heat pump comprises compressor (1), four-way change-over valve (10), condenser (2), evaporimeter (4), condensation heat recoverer (5) and throttle part (9), and described condensation heat recoverer (5) is arranged on new wind air outlet place; Described air exhaust part is performed by exhaust blower (3); Described surface-type heat exchanger is arranged on new wind air inlet; Described Fresh air handing part is containing new blower fan (6) and humidifier (12);
The c interface of described four-way change-over valve (10) is connected with one end of described condenser (2), a interface is connected with the exhaust outlet of described compressor (1), b interface is connected with the air entry of described compressor (1), d interface is connected with the one end of described evaporimeter (4), and the other end of described condenser (2) is connected with the other end of described evaporimeter (4) by throttle part (9);
Magnetic valve a (8) is also connected with between described condenser (2) and described throttle part (9), described magnetic valve a (8) two ends are parallel with described condensation heat recoverer (5), wherein, one end that described magnetic valve a (8) is connected with described condenser (2) is connected with described condensation heat recoverer (5) by magnetic valve b (7);
The new blower fan (6) of described Fresh air handing part is arranged on described new wind air outlet place, and described humidifier (12) is arranged between described evaporimeter (4) and described condensation heat recoverer (5); Exhaust blower (3) the air draft air outlet disposed in the interior place of described air exhaust part;
When outdoor air is hot humid air, open described compressor (1), a, c orifice of described four-way change-over valve (10), b, d orifice, the described surface-type heat exchanger (11) that outdoor new wind first runs through chilled water carries out pre-dehumidified, again through described evaporimeter (4) cooling and degree of depth dehumidifying further, then after described condensation heat recoverer (5) heats up, send into indoor; If new wind leaving air temp is too low, described magnetic valve b (7) need be opened, described magnetic valve a (8) is closed, and makes described condensation heat recoverer (5) raise new wind leaving air temp and reduce relative humidity; If new wind leaving air temp is too high, then need described magnetic valve a (8) to open, described magnetic valve b (7) is closed, and condensation heat recoverer (5) is not worked;
When outdoor air is low temperature dry air, open described compressor (1), a, d orifice of described four-way change-over valve (10), b, c orifice, realized the mutual conversion of evaporimeter and condenser by described four-way change-over valve; The new wind of open-air seasoning, low temperature first after described surface-type heat exchanger (11) preheating that superheated water runs, then is sent into indoor after described evaporimeter (4) and the further intensification humidification of described humidifier (12); Indoor hot and humid air is discharged outdoor after described condenser (2) cooling; Described magnetic valve a (8) is opened, and described magnetic valve b (7) is closed, and described condensation heat recoverer (5) does not work;
Summer and autumn season, when outdoor air humiture is applicable to, under central air-conditioning cooling-water machine ruuning situation, close the compressor (1) of heat pump, the described surface-type heat exchanger (11) that new wind is run by chilled water overcomes new wind load; In central air-conditioning cooling-water machine shutdown situation, new wind overcomes new wind and indoor load by the operation of described heat pump, when indoor temperature and humidity is too low, close the compressor (1) of described heat pump, the air indoor outside discharge chamber and enter indoor air outdoor and carry out ventilation;
Change according to the season in Winter-Spring, when outside air temperature is applicable to, under central water-heating machine ruuning situation, close the compressor (1) of described heat pump, the described surface-type heat exchanger (11) that new wind is run by hot water overcomes new wind load; In central water-heating machine shutdown situation; new wind overcomes new wind and indoor load by the operation of described heat pump; when indoor temperature and humidity is too high; close the compressor (1) of described heat pump, the air indoor outside discharge chamber and enter indoor air outdoor and carry out ventilation.
CN201210163979.5A 2012-05-24 2012-05-24 Double-cold-source heat pump total heat recovery humidity regulating and temperature controlling fresh air unit and control method thereof CN102705920B (en)

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CN103115419B (en) * 2013-03-04 2015-03-18 海信科龙电器股份有限公司 Energy-saving device used for air-conditioner
CN103994505A (en) * 2014-04-01 2014-08-20 侴乔力 Exhaust air source heat pump fresh air driving system
CN103925662A (en) * 2014-04-01 2014-07-16 侴乔力 Fresh air system driven by exhaust air source heat pump
CN103912947B (en) * 2014-04-13 2018-03-06 荣国华 For fan coil and the heat pump of heat recovery fresh air conditioning group
CN104501322B (en) * 2015-01-12 2017-04-05 重庆大学 A kind of absorption internally-cooled solution dehumidifying system
CN105135554A (en) * 2015-09-17 2015-12-09 丛旭日 Pre-cooling energy-saving dehumidifying system and method
CN106895520A (en) * 2017-02-15 2017-06-27 南京腾亚睿尼环境科技有限公司 A kind of air source heat pump constant temperature, constant humidity, permanent oxygen air-conditioner set
CN107166588B (en) * 2017-06-01 2020-06-16 清华大学 Temperature and humidity independent control air conditioning system capable of precooling by utilizing high-temperature cold water
CN107883744B (en) * 2017-10-31 2020-06-12 江苏天舒电器有限公司 Control method of self-adaptive and self-adjusting heat pump hot blast stove control system

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP3044409B2 (en) * 1991-03-25 2000-05-22 清水建設株式会社 Air conditioning system
CN201281431Y (en) * 2008-09-11 2009-07-29 同方人工环境有限公司 Thermal recovery fresh air unit with distributed cold and thermal sources
CN201311008Y (en) * 2008-11-25 2009-09-16 冉春雨 Air source heat pump fresh air unit for recovery of waste heat of air conditioners in cold regions
CN101614423A (en) * 2009-07-14 2009-12-30 苏州大学 A kind of heat recovery fresh air unit
CN101737877A (en) * 2009-10-27 2010-06-16 南通华信中央空调有限公司 Moisture-absorption fresh air handling unit of condenser for recovering exhaust air heat
CN202692282U (en) * 2012-05-24 2013-01-23 吕智 Double-cold-source heat pump total heat recovery humidity-regulating temperature-controlling fresh air set and control mode thereof

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1275913A3 (en) * 2001-06-26 2003-08-13 Mitsubishi Heavy Industries, Ltd. Multiform gas heat pump type air conditioning system

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP3044409B2 (en) * 1991-03-25 2000-05-22 清水建設株式会社 Air conditioning system
CN201281431Y (en) * 2008-09-11 2009-07-29 同方人工环境有限公司 Thermal recovery fresh air unit with distributed cold and thermal sources
CN201311008Y (en) * 2008-11-25 2009-09-16 冉春雨 Air source heat pump fresh air unit for recovery of waste heat of air conditioners in cold regions
CN101614423A (en) * 2009-07-14 2009-12-30 苏州大学 A kind of heat recovery fresh air unit
CN101737877A (en) * 2009-10-27 2010-06-16 南通华信中央空调有限公司 Moisture-absorption fresh air handling unit of condenser for recovering exhaust air heat
CN202692282U (en) * 2012-05-24 2013-01-23 吕智 Double-cold-source heat pump total heat recovery humidity-regulating temperature-controlling fresh air set and control mode thereof

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
JP特许第3044409号B2 2000.05.22 *

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