CN2665580Y - Parallel connection heat pump conditioning unit - Google Patents
Parallel connection heat pump conditioning unit Download PDFInfo
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- CN2665580Y CN2665580Y CN 200320125192 CN200320125192U CN2665580Y CN 2665580 Y CN2665580 Y CN 2665580Y CN 200320125192 CN200320125192 CN 200320125192 CN 200320125192 U CN200320125192 U CN 200320125192U CN 2665580 Y CN2665580 Y CN 2665580Y
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Abstract
The utility model relates to a parallel heat pump temperature and humidity adjusting unit, belonging to a technical field of refrigeration, air conditioning and de-humidification, in the utility model a compressor, an outdoor heat exchanger, first and second indoor heat exchangers and throttling devices are connected to form a refrigeration circulation by refrigerant pipelines, wherein the outdoor heat exchanger is connected in parallel with the two branch circuits of the indoor heat exchanger, the utility model further comprises a four-way valve, therefore the utility model can realize four different operation modes by the four-way valve, and also realize stopples rapid defrosting, thereby meeting the requirement of the large range change of full-year operational cold/hot load, micro-adjustment is made by the energization and de-energization of the two solenoids on the two parallel heat exchangers and the adjustment of air or water amount of the outdoor heat exchanger, so as to meet the need of different wet/cold/hot load, so that the indoor temperature and humidity can be controlled in the preset range well. The utility model has wide application range, and can perform full-year operation temperature and humidity adjustment in most regions of our country, thereby improving utilization ratio of equipments.
Description
Technical field
The utility model relates to a kind of freeze drying equipment, relates in particular to a kind of pump type heat temperature adjusting and dehumidifying equipment, belongs to refrigeration, air-conditioning and dehumidifying technology field.
Background technology
Cooled dehumidifier unit dehumidifies to air cooling-down with evaporimeter, and the condensation heat of recovery system, remedy in the air because dispersed heat during cooling and dehumidifying is a kind of energy-efficient dehumidification mode, be widely used in the removal moisture drying of grain, timber etc. and the dehumidifying in high humidity space and controlled with temperature.
At present the cooled dehumidifier unit of China mainly contains two kinds of heating type and temperature-adjusting types.The heating type dehumidifier is made of an indoor condenser and an indoor evaporator, when giving indoor the dehumidifying, also will be dispersed into condensation heat and indoorly heat to room air.In order further to improve heat capacity and leaving air temp, set up an evaporimeter in parallel outdoor with indoor evaporator, such dehumidifier can carry out heat supply to indoor by being used alternatingly the indoor and outdoor evaporimeter, also can realize dehumidification function, but can not realize the indoor temperature control purpose, can only be used for the occasion of indoor needs heating or high-temperature drying chamber.Temperature regulating dehumidifier is on the basis of heating type dehumidifier, at condenser of outdoor increase, connect or parallel connection with indoor condenser, (Chinese utility model patent such as Wang Wenzhi as shown in Figure 1 disclosed " a kind of train air-conditioning machine that can dehumidify continuously ", the patent No.: 98215431.3) be exactly a kind of double-condenser type temperature-adjustable dehumidifier in parallel, by outdoor heat exchanger 1, indoor second heat exchanger 2, indoor second heat exchanger control magnetic valve 3, throttling arrangement 4, indoor first heat exchanger 5 and compressor 6 etc. are formed by connecting, and wherein indoor second heat exchanger 2 and outdoor heat exchanger 1 parallel connection are as condenser, and indoor first heat exchanger 5 is an evaporimeter.Air is warm through being undertaken by indoor second heat exchanger 2 behind indoor first heat exchanger, 5 cool-down dehumidifications again, and controls indoor air temperature by the break-make of regulating magnetic valve 3.Such system is because outdoor heat exchanger 1 will be born many condensation heat; the condensation heat that indoor second heat exchanger 2 reclaims seldom; therefore can only be applicable in indoor refrigeration or the smaller situation of thermic load of needing; when indoor thermic load is bigger; system's heat capacity deficiency; can not meet the demands; and when indoor temperature is relatively lower; the 5 easy frostings of indoor first heat exchanger; need to adopt and shut down defrosting or adopt auxiliary electrically heated mode to defrost; regulate temperature by the break-make of magnetic valve 3 in addition, frequent break-make makes magnetic valve 3 be very easy to damage.
In sum, can only be applicable to the requirement of comparison particular environment in the present dehumidification and temperature adjustment scheme, regulating power is poor, the scope of application is little, and China's climate type is various, and most of area summer in winter temperature difference is big, hot/cold/humidity load changes obviously in time, such system can not well satisfy actual needs, and annual service time is short, has also caused the idle and waste of equipment.
The utility model content
The purpose of this utility model provides a kind ofly can carry out heat supply, refrigeration and dehumidifying to satisfy the pump type heat conditioning unit in parallel of indoor temperature and humidity requirement to indoor under the inside and outside temperature of different chamber, to improve the performance of dehumidification and temperature adjustment system, enlarge the scope of application of dehumidification and temperature adjustment system.
The utility model is achieved by the following technical solution:
A kind of parallel connection type heat pump conditioning unit, by compressor, outdoor heat exchanger, indoor second heat exchanger, indoor first heat exchanger and throttling arrangement connect into a kind of refrigeration cycle by refrigerant line, wherein two branch roads of outdoor heat exchanger and indoor second heat exchanger are in parallel, and the magnetic valve be used for controlling the branch road break-make is installed on the branch road of indoor second heat exchanger, it is characterized in that: this unit also comprises a cross valve, the exhaust outlet of described compressor links to each other with a mouth of cross valve by refrigerant line, and the air entry of compressor links to each other with the c mouth of cross valve by pipeline; Link to each other with the b mouth of cross valve by refrigerant line one end after described outdoor heat exchanger and the indoor second heat exchanger parallel connection, its other end links to each other with throttling arrangement; The magnetic valve that is used for controlling this branch road break-make is installed on the branch road of outdoor heat exchanger, and described indoor heat exchanger links to each other with the d mouth of cross valve by refrigerant line one end, and the other end links to each other with throttling arrangement.
The utility model freezes by cross valve and the heating mode conversion, can satisfy the requirement of whole year operation cooling and heating load wide variation, and the adjusting of the break-make by two heat exchangers in parallel branch roads and the outdoor heat exchanger air quantity or the water yield is carried out trace and is regulated, can satisfy the needs of DIFFERENT WET/cold/thermic load, make to be controlled in the setting range preferably indoor temperature and humidity.The utility model adopts the method for cross valve reverse cycle defrost, realizes not shutting down quickly defrosting.The utility model is applied widely, and regulating power is strong, can carry out humiture at the most of regional whole year operations of China and regulate, and has improved usage ratio of equipment.
Description of drawings
Fig. 1 is a double-condenser type temperature-adjustable dehumidifier systematic schematic diagram in parallel in the prior art.
Fig. 2 is a parallel connection type heat pump conditioning unit schematic diagram of the present utility model.
Fig. 3 is air-cooled parallel connection type heat pump conditioning set structure schematic diagram.
Fig. 4 is a water-cooled parallel connection type heat pump conditioning set structure schematic diagram.
The specific embodiment
Below in conjunction with accompanying drawing enforcement of the present utility model is further described.
As shown in Figure 2, the utility model is mainly by compressor 6, cross valve 8, throttling arrangement 4, outdoor heat exchanger 1, outdoor heat exchanger control magnetic valve 7, indoor first heat exchanger 5, indoor second heat exchanger 2, indoor second heat exchanger control magnetic valve 3 and indoor fan 9 constitute; The exhaust outlet of compressor 6 links to each other with a mouth of cross valve 8 by refrigerant line, the air entry of compressor 6 links to each other with the c mouth of cross valve 8 by pipeline, outdoor heat exchanger 1 adopts form in parallel to link to each other with the b mouth of cross valve 8 by refrigerant line one end with indoor second heat exchanger 2, its other end with link to each other with throttling arrangement 4; The magnetic valve 7 and 3 that is used for controlling two branch road break-makes is installed respectively on the branch road of outdoor heat exchanger 1 and 2 two parallel connections of indoor second heat exchanger, and indoor heat exchanger 5 is by the d mouth of refrigerant line one end and cross valve 8, and the other end links to each other with throttling arrangement 4.Room air under the effect of indoor fan 9 successively by indoor first heat exchanger 5 and indoor second heat exchanger 2 again in the return chamber.
(i) cool-down dehumidification pattern
When indoor temperature and humidity all than higher, and indoor refrigeration duty is when bigger, system runs on the cool-down dehumidification pattern.This moment, cross valve 8 was not charged, and a mouth of cross valve 8 is communicated with the b mouth, the c mouth is communicated with the d mouth, and magnetic valve 3 cuts out, and magnetic valve 7 is opened, and outdoor heat exchanger 1 is a condenser, and indoor first heat exchanger 5 is an evaporimeter.After cold-producing medium comes out from compressor 6, flow into a mouth of cross valve 8, flow into condensation the outdoor heat exchanger 1 from the b mouth of cross valve 8, again through after indoor first heat exchanger 5 of inflow is evaporated to gas after magnetic valve 7 and throttling arrangement 4 throttlings, flow into the d mouth of cross valve 8, c mouth from cross valve 8 flows back to compressor 6 again, and the flow of refrigerant direction is shown in solid arrow among Fig. 2.Because the refrigerant flow path of indoor second heat exchanger 2 is closed by magnetic valve 3, room air becomes in the air return chamber of low temperature and low humidity only by indoor first heat exchanger, 5 cool-down dehumidifications.Under this pattern, the air quantity or the water yield that can also conditioning chamber external heat exchanger 1 be further regulated refrigerating capacity and moisture removal, and refrigerating capacity and moisture removal all rise along with the increase of outdoor heat exchanger 1 air quantity or the water yield.
(ii) temperature adjusting and dehumidifying pattern
When indoor humidity and humidity load all than higher, and indoor refrigeration duty is when smaller, system runs on the temperature adjusting and dehumidifying pattern.This moment, cross valve 8 was not charged, and a mouth of cross valve 8 is communicated with the b mouth, the c mouth is communicated with the d mouth, and magnetic valve 3 and 7 is all opened, and outdoor heat exchanger 1 and indoor second heat exchanger 2 are the condenser of two parallel connections, and indoor first heat exchanger 5 is an evaporimeter.After cold-producing medium comes out from compressor 6, flow into a mouth of cross valve 8, flow out from the b mouth of cross valve 8, flow into respectively then in indoor second heat exchanger 2 and the outdoor heat exchanger 1 after the condensation, after converging through magnetic valve 3 and 7 respectively more again through after flowing into indoor first heat exchanger 1 after throttling arrangement 4 throttlings and being evaporated to gas, flow into the d mouth of cross valve 8, the c mouth from cross valve 8 flows back to compressor 6 again, and the flow of refrigerant direction is shown in solid arrow among Fig. 2.Owing to also have high temperature refrigerant to flow through in indoor second heat exchanger 2, room air is only by behind indoor first heat exchanger, 5 cool-down dehumidifications, after indoor second heat exchanger 2 of process carries out heat again, in the air return chamber.Under this pattern, the air quantity and the water yield that can also conditioning chamber external heat exchanger 1 be regulated the distribution of two condenser heat exchange amounts, further heat again in the control room, thus reach the purpose of control indoor air temperature.Along with the increase of outdoor heat exchanger 1 air quantity or the water yield, the heat exchange amount of outdoor heat exchanger 1 rises, and the heat exchange amount of indoor second heat exchanger 2 is the reduction of heat again of air.
Dehumidification mode (iii) heats up
When indoor humidity and humidity load all than higher, but indoor temperature is low and thermic load when smaller, system runs on the intensification dehumidification mode.This moment, cross valve 8 was not charged, and a mouth of cross valve 8 is communicated with the b mouth, the c mouth is communicated with the d mouth, and magnetic valve 3 is opened, and magnetic valve 7 cuts out, and indoor second heat exchanger 2 is a condenser, and indoor first heat exchanger 5 is an evaporimeter.After cold-producing medium comes out from compressor 6, flow into a mouth of cross valve 8, flow into indoor second heat exchanger 2 after the condensation from the b mouth of cross valve 8, be evaporated to gas through flowing into indoor first heat exchanger 5 after magnetic valve 3 and throttling arrangement 4 throttlings again, flow into the d mouth of cross valve 8, c mouth from cross valve 8 flows back to compressor 6 again, and the flow of refrigerant direction is shown in solid arrow among Fig. 2.Owing to also have high temperature refrigerant to flow through in indoor second heat exchanger 2, room air is only by behind indoor first heat exchanger, 5 cool-down dehumidifications, after indoor second heat exchanger 2 of process carries out heat again, in the air return chamber.Under this pattern, because the refrigerant flow path of outdoor heat exchanger 1 is turn-offed by magnetic valve 7, all condensation heat is all born by indoor second heat exchanger 2, and system condensing heat is greater than heat of evaporation, so processed air humidity decline temperature rises.
(iv) heat the damping pattern
When indoor temperature very low, and thermic load is when bigger, although relative humidity is than higher, but water capacity is lower, removes relatively difficulty of airborne moisture, but with after the air heat, under the constant situation of water capacity, the relative humidity of air just descends rapidly, therefore can pass through system's heating operation, realizes the control to indoor temperature and humidity.This moment, cross valve 8 was charged, and a mouth of cross valve 8 is communicated with the d mouth, the b mouth is communicated with the c mouth, and magnetic valve 7 is opened, and magnetic valve 3 cuts out, and outdoor heat exchanger 1 is an evaporimeter, and indoor first heat exchanger 5 is a condenser.After cold-producing medium comes out from compressor 6, flow into a mouth of cross valve 8, flow into indoor first heat exchanger 5 after the condensation from the d mouth of cross valve 8, again through after flowing into outdoor heat exchangers 1 and be evaporated to gas through magnetic valve 7 after throttling arrangement 4 throttlings, flow into the b mouth of cross valve 8, c mouth from cross valve 8 flows back to compressor 6 again, and the flow of refrigerant direction is shown in dotted arrow among Fig. 2.Under this pattern, because the refrigerant flow path of indoor second heat exchanger 2 turn-offed by magnetic valve 3, room air is only by after 5 heating of indoor first heat exchanger, do not carry out after the heat exchange in the return chamber through indoor second heat exchanger 2.
(v) automatic defrosting
The utility model adopts the method for cross valve reverse cycle defrost, realizes not shutting down quickly defrosting.
When system runs on pattern (i)-(iii), indoor first heat exchanger 5 is an evaporimeter, when the evaporator surface temperature is lower than 0 ℃, enter the relative air humidity of evaporimeter 5 when big, airborne moisture may be in the evaporator external frosting, after frost reaches certain thickness, make the air side pressure loss rise, air mass flow reduces, and the heat exchange weak effect need defrost.After the air side pressure loss surpasses setting value, give cross valve 8 energisings, make unit operation in heating the damping pattern (iv), indoor first heat exchanger 5 is as condenser, after the entering of high temperature refrigerant made that frost melts rapidly, cross valve 8 cut off the power supply again, recovers original operational mode.
When running on, system heats the damping pattern (iv) the time, outdoor heat exchanger 1 is an evaporimeter, when outside air temperature low humidity height and evaporator surface temperature are lower than 0 ℃, the also possibility frosting of outdoor heat exchanger outer surface, after frost reaches certain thickness, make the air side pressure loss rise, air mass flow reduces, the heat exchange weak effect need defrost.After the air side pressure loss surpasses setting value, give cross valve 8 outages, make unit operation (ii) in the temperature adjusting and dehumidifying pattern, outdoor heat exchanger 1 is as condenser, and entering of high temperature refrigerant makes frost melt rapidly, and indoor second heat exchanger 2 is also as condenser, prevent by in the direct inlet chamber of air of indoor first heat exchanger 5 coolings, after frost was removed fully, cross valve 8 was switched on again, recovered to heat the temperature adjustment pattern.
Specific embodiment 1: air-cooled parallel connection type heat pump conditioning unit
The structural representation of Fig. 3 air-cooled parallel connection type heat pump conditioning unit for the utility model adopts
As shown in Figure 3, air-cooled parallel connection type heat pump conditioning unit is by compressor 6, cross valve 8, throttling arrangement 4, outdoor heat exchanger 1, outdoor heat exchanger control magnetic valve 7, indoor first heat exchanger 5, indoor second heat exchanger 2, the basic elements of character such as indoor second heat exchanger control magnetic valve 3 and indoor fan 9 are formed by connecting by pipeline.The exhaust outlet of compressor 6 links to each other with a mouth of cross valve 8 by refrigerant line, the air entry of compressor 6 links to each other with the c mouth of cross valve 8 by pipeline, outdoor heat exchanger 1 adopts form in parallel to link to each other with the b mouth of cross valve by refrigerant line one end with indoor second heat exchanger 2, the other end links to each other with throttling arrangement 4, the magnetic valve 7 and 3 that is used for controlling two branch road break-makes is installed respectively on the branch road of outdoor heat exchanger 1 and 2 two parallel connections of indoor second heat exchanger, indoor first heat exchanger 5 links to each other with the d mouth of cross valve 8 by refrigerant line one end, and the other end links to each other with throttling arrangement 4.Room air under the effect of indoor fan 9 successively by indoor first heat exchanger 5 and indoor second heat exchanger 2 again in the return chamber.
Wherein outdoor heat exchanger 1 adopts air cooling heat exchanger, and outdoor fan 10 can adopt speed-changing draught fan or a few typhoon machine, comes the air quantity of conditioning chamber external heat exchanger by the platform number of regulating rotation speed of fan or unlatching.
Too high for anti-locking system internal pressure, guarantee that at compressor outlet setting pressure controller 11 system's internal pressure is no more than the scope of setting.
For adaptability and the adjustable range that improves unit, throttling arrangement 4 adopts the suction superheat of heating power expansion valve or electric expansion valve automatic control compressor, vapour liquid separator 12 actings in conjunction with compressor 6 air entries, prevent that liquid refrigerant from directly getting back to compressor 6 and causing damage to compressor 6, and before throttling arrangement 4, high pressure receiver 13 is installed and device for drying and filtering 14 prevents that gaseous refrigerant or impurity from entering throttling arrangement 4.At preceding installation high pressure receiver of throttling arrangement (4) (13) and device for drying and filtering (14), in high pressure receiver (13) import check valve (15,17) is installed, in throttling arrangement (4) outlet check valve (16,18) is installed and is made that cold-producing medium all is successively by high pressure receiver 13, device for drying and filtering 14 and throttling arrangement 4 when freezing or heating.
In order to prevent that dust in air from dropping on indoor first heat exchanger 5 and indoor second heat exchanger 2, install air cleaner 19 additional at indoor first heat exchanger, 5 air side inlet.And in the outlet of indoor first heat exchanger, 5 air side water fender 20 is installed and is prevented from directly to be taken away by air by the moisture that indoor first heat exchanger 5 is removed.
Air-cooled parallel connection type heat pump conditioning unit still can be realized above-mentioned cool-down dehumidification, temperature adjusting and dehumidifying, dehumidifying heats up, several operational modes such as heat supply damping and automatic defrosting, under various operational modes, rotating speed by regulating outdoor fan 10 or open the air quantity that the platform number comes conditioning chamber external heat exchanger 1, and then refrigerating capacity, heating capacity and the moisture removal of unit are regulated temperature and humidity in the more accurate control room.
With compressor 6, cross valve 8, indoor fan 9, magnetic valve 3 and 7, the controller of outdoor fan 10 grades all is installed in the electric cabinet 21.
Specific embodiment 2: water-cooled parallel connection type heat pump conditioning unit
Fig. 4 adopts the structural representation of water-cooled parallel connection type heat pump conditioning unit for the utility model.
As shown in Figure 4, the parts composition of water-cooled parallel connection type heat pump conditioning unit is identical with air-cooled parallel connection type heat pump conditioning unit with annexation, and just outdoor heat exchanger 1 adopts water cooling heat exchanger, and outdoor fan 10 is replaced by the water pump among Fig. 4 22 among Fig. 3.
Water-cooled parallel connection type heat pump conditioning unit still can be realized above-mentioned cool-down dehumidification, temperature adjusting and dehumidifying, dehumidifying heats up, several operational modes such as heat supply damping and automatic defrosting, under various operational modes, the water yield of coming conditioning chamber external heat exchanger 1 by the rotating speed of regulating water pump 22, and then refrigerating capacity, heating capacity and the moisture removal of unit regulated temperature and humidity in the more accurate control room.
Claims (8)
1. parallel connection type heat pump conditioning unit, by compressor (6), outdoor heat exchanger (1), indoor second heat exchanger (2), indoor first heat exchanger (5) and throttling arrangement (4) connect into a kind of refrigeration cycle by refrigerant line, wherein (2) two branch roads of outdoor heat exchanger (1) and indoor second heat exchanger are in parallel, and the magnetic valve (3) be used for controlling the branch road break-make is installed on the branch road of indoor second heat exchanger (2), it is characterized in that: this unit also comprises a cross valve (8), the exhaust outlet of described compressor (6) links to each other by a mouth of refrigerant line with cross valve (8), and the air entry of compressor links to each other by the c mouth of pipeline with cross valve (8); Described outdoor heat exchanger (1) links to each other with the b mouth of cross valve by refrigerant line one end with indoor second heat exchanger (2) back in parallel, and its other end links to each other with throttling arrangement (4); The magnetic valve (7) that is used for controlling this branch road break-make is installed on the branch road of outdoor heat exchanger (1), and described indoor heat exchanger (5) links to each other with the d mouth of cross valve (8) by refrigerant line one end, and the other end links to each other with throttling arrangement (4).
2. according to the described parallel connection type heat pump of claim 1 conditioning unit, it is characterized in that: pressure controller (11) is installed in described compressor (6) outlet.
3. according to the described parallel connection type heat pump of claim 1 conditioning unit, it is characterized in that: be equipped with at described compressor (6) inlet and prevent that liquid refrigerant from getting back to the vapour liquid separator of compressor (12).
4. according to the described parallel connection type heat pump of claim 1 conditioning unit, it is characterized in that: described throttling arrangement (4) adopts capillary, heating power expansion valve or electric expansion valve.
5. according to the described parallel connection type heat pump of claim 1 conditioning unit, it is characterized in that: at indoor first heat exchanger (5) air side inlet filter (19) is installed, water fender (20) is installed in the outlet of indoor first heat exchanger (5) air side.
6. according to the described a kind of parallel connection type heat pump conditioning unit of claim 1, it is characterized in that: at preceding installation high pressure receiver of throttling arrangement (4) (13) and device for drying and filtering (14), in high pressure receiver (13) import check valve (15,17) is installed, check valve (16,18) is installed in throttling arrangement (4) outlet.
7. according to the described parallel connection type heat pump of the arbitrary claim of claim 1-6 conditioning unit, it is characterized in that: described outdoor heat exchanger (1) adopts air cooling heat exchanger.
8 according to the described parallel connection type heat pump of the arbitrary claim of claim 1-6 conditioning unit, it is characterized in that: described outdoor heat exchanger (1) adopts water cooling heat exchanger.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 200320125192 CN2665580Y (en) | 2003-12-05 | 2003-12-05 | Parallel connection heat pump conditioning unit |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 200320125192 CN2665580Y (en) | 2003-12-05 | 2003-12-05 | Parallel connection heat pump conditioning unit |
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| Publication Number | Publication Date |
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| CN2665580Y true CN2665580Y (en) | 2004-12-22 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 200320125192 Expired - Lifetime CN2665580Y (en) | 2003-12-05 | 2003-12-05 | Parallel connection heat pump conditioning unit |
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Cited By (14)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN100370200C (en) * | 2005-02-04 | 2008-02-20 | 松下电器产业株式会社 | Air-conditioner |
| CN101196355B (en) * | 2007-12-07 | 2010-06-16 | 广东五星太阳能有限公司 | Multifunctional solar heat pump |
| CN102155773A (en) * | 2011-05-12 | 2011-08-17 | 宁波工程学院 | Heat-recovery type heat pump air conditioning system |
| CN101706136B (en) * | 2009-11-21 | 2012-04-18 | 青岛大学 | Solution temperature and humidity adjustment air treatment system |
| CN103912937A (en) * | 2014-04-25 | 2014-07-09 | 江苏兆胜空调有限公司 | Marine multi-partition purification air conditioning unit |
| CN104110748A (en) * | 2013-04-17 | 2014-10-22 | 三菱电机株式会社 | Air conditioning device |
| CN105637302A (en) * | 2013-10-01 | 2016-06-01 | 株式会社德山科特兰 | Thermo-hygrostat using compressor discharged heat source |
| CN107676902A (en) * | 2017-10-27 | 2018-02-09 | 国安瑞（北京）科技有限公司 | Air-conditioning system |
| CN107747806A (en) * | 2017-10-27 | 2018-03-02 | 国安瑞（北京）科技有限公司 | Air-conditioning system |
| CN107940636A (en) * | 2017-10-27 | 2018-04-20 | 国安瑞（北京）科技有限公司 | Air-conditioning system |
| CN107975869A (en) * | 2017-10-27 | 2018-05-01 | 国安瑞（北京）科技有限公司 | Air-conditioning system |
| CN108332327A (en) * | 2018-03-01 | 2018-07-27 | 清华大学 | A kind of airhandling equipment |
| CN108603702A (en) * | 2015-07-14 | 2018-09-28 | 株式会社电装 | Heat pump cycle |
| CN113669860A (en) * | 2021-07-29 | 2021-11-19 | 中洁环境科技(西安)集团有限公司 | Heat pump type fresh air integrated dehumidifier and control method and device thereof |
-
2003
- 2003-12-05 CN CN 200320125192 patent/CN2665580Y/en not_active Expired - Lifetime
Cited By (16)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN100370200C (en) * | 2005-02-04 | 2008-02-20 | 松下电器产业株式会社 | Air-conditioner |
| CN101196355B (en) * | 2007-12-07 | 2010-06-16 | 广东五星太阳能有限公司 | Multifunctional solar heat pump |
| CN101706136B (en) * | 2009-11-21 | 2012-04-18 | 青岛大学 | Solution temperature and humidity adjustment air treatment system |
| CN102155773A (en) * | 2011-05-12 | 2011-08-17 | 宁波工程学院 | Heat-recovery type heat pump air conditioning system |
| CN104110748A (en) * | 2013-04-17 | 2014-10-22 | 三菱电机株式会社 | Air conditioning device |
| CN105637302A (en) * | 2013-10-01 | 2016-06-01 | 株式会社德山科特兰 | Thermo-hygrostat using compressor discharged heat source |
| CN103912937A (en) * | 2014-04-25 | 2014-07-09 | 江苏兆胜空调有限公司 | Marine multi-partition purification air conditioning unit |
| CN108603702A (en) * | 2015-07-14 | 2018-09-28 | 株式会社电装 | Heat pump cycle |
| CN107747806A (en) * | 2017-10-27 | 2018-03-02 | 国安瑞（北京）科技有限公司 | Air-conditioning system |
| CN107940636A (en) * | 2017-10-27 | 2018-04-20 | 国安瑞（北京）科技有限公司 | Air-conditioning system |
| CN107975869A (en) * | 2017-10-27 | 2018-05-01 | 国安瑞（北京）科技有限公司 | Air-conditioning system |
| CN107676902A (en) * | 2017-10-27 | 2018-02-09 | 国安瑞（北京）科技有限公司 | Air-conditioning system |
| CN107676902B (en) * | 2017-10-27 | 2020-06-16 | 国安瑞（北京）科技有限公司 | Air conditioning system |
| CN108332327A (en) * | 2018-03-01 | 2018-07-27 | 清华大学 | A kind of airhandling equipment |
| CN108332327B (en) * | 2018-03-01 | 2023-11-10 | 清华大学 | Air treatment equipment |
| CN113669860A (en) * | 2021-07-29 | 2021-11-19 | 中洁环境科技(西安)集团有限公司 | Heat pump type fresh air integrated dehumidifier and control method and device thereof |
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