US20100083683A1 - Refrigeration air dryer - Google Patents

Refrigeration air dryer Download PDF

Info

Publication number
US20100083683A1
US20100083683A1 US12/557,750 US55775009A US2010083683A1 US 20100083683 A1 US20100083683 A1 US 20100083683A1 US 55775009 A US55775009 A US 55775009A US 2010083683 A1 US2010083683 A1 US 2010083683A1
Authority
US
United States
Prior art keywords
air
refrigerant
temperature
reheater
cooler
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.)
Abandoned
Application number
US12/557,750
Other languages
English (en)
Inventor
Hideaki Aono
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
SMC Corp
Original Assignee
SMC Corp
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by SMC Corp filed Critical SMC Corp
Assigned to SMC CORPORATION reassignment SMC CORPORATION ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: AONO, HIDEAKI
Publication of US20100083683A1 publication Critical patent/US20100083683A1/en
Abandoned legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B01—PHYSICAL OR CHEMICAL PROCESSES OR APPARATUS IN GENERAL
    • B01D—SEPARATION
    • B01D53/00—Separation of gases or vapours; Recovering vapours of volatile solvents from gases; Chemical or biological purification of waste gases, e.g. engine exhaust gases, smoke, fumes, flue gases, aerosols
    • B01D53/26—Drying gases or vapours
    • B01D53/265—Drying gases or vapours by refrigeration (condensation)
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B29/00—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously

Definitions

  • the present invention relates to a refrigeration air dryer which dehumidifies compressed air by condensing moisture in the compressed air by cooling the compressed air.
  • the moisture included in the compressed air is preferably removed beforehand.
  • a refrigeration air dryer is employed.
  • FIG. 2 shows a circuit of a refrigerant system and an air system in a conventional refrigeration air dryer.
  • the refrigerant system in refrigeration air dryer includes a refrigerant compressor 10 , a condenser 11 which condenses a high-temperature refrigerant compressed by the refrigerant compressor 10 and transmitted via a high-temperature refrigerant pipe 22 , an expansion valve 12 which decompresses, by adiabatic expansion, the refrigerant thus condensed by the condenser 11 , and a cooler 13 which again cools the air, which has been preliminarily cooled by a first reheater 14 included in the air system, using the low-temperature refrigerant transmitted from the expansion valve 12 , so as to dehumidifies the air.
  • the refrigerant system is configured such that the refrigerant from the cooler 13 is returned to the refrigerant compressor 10 via a return refrigerant pipe 26 .
  • the air system includes: an air inlet 20 which allows primary air, which is warm and moist and which is to be dehumidified, to flow into the air system; the reheater 14 which preliminarily cools the primary air input via the air inlet 20 by heat exchanging with the low-temperature dehumidified air after the dehumidification processing; the cooler 13 which again cools the air thus preliminarily cooled by the reheater 14 ; and a drain separator 16 which performs drain separation processing for the air thus cooled again by the cooler 13 , and transmits the air in a low-temperature dehumidified state to the reheater 14 .
  • the air system is configured such that heat exchange is performed at the reheater 14 between the dehumidified air and the primary air, thereby preliminarily cooling the primary air, and thereby raising the temperature of the low-temperature dehumidified air, following which the dehumidified air is externally discharged as secondary air.
  • the cooler 13 is connected to both the refrigerant system and the air system, and functionally connects the refrigerant system and the air system.
  • the drain separator 16 which performs the drain separation processing, includes a drain valve 15 which externally discharges resultant water drops.
  • the temperature of the high-temperature refrigerant flowing into the condenser 11 from the refrigerant compressor 10 via the high-temperature refrigerant pipe 22 is approximately 90° C.
  • the temperature of the refrigerant, which flows into the cooler 13 via the low-temperature refrigerant pipe 23 after the adiabatic expansion provided by the expansion valve 12 is approximately 5° C.
  • the temperature of the primary air, which is input to the reheater 14 via the air inlet 20 is 40° C. (rated temperature).
  • the temperature of the air, which flows through the cooler 13 via the air pipe 24 after the air has been preliminarily cooled at the reheater 14 is approximately 25° C.
  • the temperature of the dehumidified air which is transmitted to the reheater 14 via the drain separator 16 after the dehumidified air has been again cooled at the cooler 13 , is approximately 10° C.
  • the temperature of the secondary air which is externally discharged via the outlet pipe 21 after the temperature thereof has been raised at the reheater 14 , is approximately 30° C.
  • the high-temperature refrigerant pipe 22 that connects the refrigerant compressor 10 and the condenser 11 and the low-temperature refrigerant pipe 23 that connects the expansion valve 12 and the cooler 13 communicate with each other via a bypass refrigerant pipe 25 including a volume adjusting valve 17 which provides an adjustable opening.
  • the bypass refrigerant pipe 25 is provided in order to maintain the temperature of the low-temperature refrigerant such that it does not become equal to or smaller than a predetermined temperature, by mixing a portion of the high-temperature refrigerant flowing through the condenser 11 from the refrigerant compressor 10 into the low-temperature refrigerant in the low-temperature refrigerant pipe 23 , by instructing the volume adjusting valve 17 to provide a suitable opening, thereby preventing the moisture included in the moist compressed air, which flows from the reheater 14 to the cooler 13 via the air pipe 24 , from freezing due to excessive reduction in the temperature of the refrigerant flowing from the expansion valve 12 to the cooler 13 via the low-temperature refrigerant pipe 23 , in a case in which the load of the cooler 13 has become small.
  • the conventional air dryer shown in FIG. 2 has a problem in that the performance of the reheater drops depending upon the conditions of use. Specific description will be made.
  • the purposes of employing the reheater 14 are as follows.
  • the compressed air input to the air dryer is preliminarily cooled by the reheater, thereby reducing the load applied to the refrigeration circuit (refrigerant system) (the load of the refrigerant circuit is reduced, thereby reducing energy consumption).
  • the temperature of the compressed air dehumidified by the air dryer is raised using the heat of the primary air input anew from the air inlet, thereby preventing occurrence of dew condensation at the secondary air pipe in the air dryer.
  • the performance of the reheater drops, leading to a situation in which the temperature of the secondary air, which is to be discharged via the outlet pipe 21 , cannot be raised to a temperature at which dew condensation at the outlet pipe 21 can be prevented.
  • the reheater is provided between the high-temperature refrigerant pipe 22 , which transmits the refrigerant compressed by the refrigerant compressor 10 to the condenser 11 , and the outlet pipe 21 via which the dehumidified air from the drain separator 16 is externally discharged, thereby enabling the temperature of the secondary air discharged from the outlet pipe 21 to be sufficiently raised.
  • the air input via the air inlet 20 (primary air) cannot be preliminarily cooled. Accordingly, all of the thermal load is applied to the refrigeration circuit (refrigerant system), leading to reduction in the air throughput of the air dryer. In a case in which the air throughput is increased to that of the air dryer shown in FIG. 2 , there is a need to increase the scale of the refrigeration circuit.
  • the methods for reducing energy consumption employed in such conventional refrigeration air dryers include: a method in which the capacity of the condenser is increased: a method in which the amount of the refrigerant for the condenser is increased; a method in which the temperature of the refrigerant thereof is lowered: etc.
  • Such methods leads to disadvantages, examples of which include: an increased scale of the dryer; an increased scale of refrigeration equipment (air conditioner, chiller, cooling tower, etc.), an increased energy consumption of the refrigeration equipment.
  • the refrigerant is condensed by air cooling or water cooling.
  • the heat exchanger duty Q 1 of the cooler 13 which corresponds to the refrigeration capacity of the refrigeration air dryer is predetermined.
  • the ambient temperature around the condenser is predetermined, and in the case of employing a water-cooled condenser, the temperature of coolant water is predetermined. Accordingly, the capacity of the condenser 11 is predetermined.
  • the present invention is a technical purpose of the present invention to provide high dehumidification performance with small electric power consumption by reducing the heat exchanger duty Q 3 of the condenser in the refrigeration air dryer, i.e., the heat quantity discharged from the condenser, effectively using energy in the conventional refrigeration air dryer, thereby providing an energy-saving refrigeration air dryer.
  • a technical purpose of the present invention to provide a refrigeration air dryer which exhibits stable dehumidification performance even in a case in which the load of the compressed air to be dehumidified is great (in a case in which the temperature, the humidity, or the flow of the compressed air is great, etc.), and which is capable of preventing occurrence of dew condensation in a sure manner at the outlet pipe via which the dehumidified secondary air is externally discharged even in a case in which the temperature of the primary air is low.
  • a refrigeration air dryer including: a refrigerant system which includes a refrigerant compressor, a condenser which condenses a high-temperature refrigerant compressed by the refrigerant compressor, a decompressing mechanism which decompresses, by adiabatic expansion, the refrigerant which has been condensed by the condenser, so as to lower the temperature thereof, and a cooler which again cools the air, which has been preliminarily cooled by a first reheater in an air system, using the low-temperature refrigerant transmitted from the decompressing mechanism, so as to dehumidify the air, and which is configured such that the refrigerant transmitted from the cooler is returned to the refrigerant compressor; and the air system which includes an air inlet which allows warm and moist compressed air, which is to be dehumidified, to be input as primary air, the first reheater which preliminarily cools the primary air and
  • the refrigeration air dryer further includes a second reheater which exchange heat between the dehumidified air, of which the temperature has been raised at the first reheater by exchanging heat with the primary air, and the high-temperature refrigerant compressed by the refrigerant compressor.
  • the refrigeration air dryer is configured such that the dehumidified air, of which the temperature has been again raised by heat exchange at the second reheater, is output as secondary air via an outlet pipe.
  • the second reheater is preferably connected between the refrigerant compressor and the condenser. Furthermore, the refrigerant transmitted from the refrigerant compressor is preferably transmitted to the condenser via the second reheater.
  • an arrangement may be made in which a high-temperature refrigerant pipe which connects the refrigerant compressor and the second reheater and a low-temperature refrigerant pipe which connects the decompressing mechanism and the cooler or a return refrigerant pipe which connects the cooler and the refrigerant compressor are connected so as to communicate with each other via a bypass refrigerant pipe including a volume adjusting valve which provides an adjustable opening, thereby allowing a portion of the high-temperature refrigerant compressed by the refrigerant compressor to directly flow into the low-temperature refrigerant pipe or the return refrigerant pipe in a case in which the load of the cooler has become small.
  • the refrigeration air dryer preferably includes a drain separator in a flow channel from the cooler up to the first reheater, which is used to perform drain separation processing for the air again cooled by the cooler.
  • the refrigeration air dryer having the above-described configuration employs a combination of the first reheater which exchanges heat between the primary air input via the air inlet and the low-temperature dehumidified air transmitted via the cooler and the second reheater which exchanges heat between the refrigerant which has become high temperature by compression at the refrigerant compressor and the dehumidified air of which the temperature has been raised by being subjected to the preliminary cooling of the primary air at the first reheater.
  • such an arrangement provides high dehumidification performance with small electric power consumption by reducing the heat exchanger duty Q 3 of the condenser in the refrigeration air dryer, i.e., the heat quantity discharged from the condenser. For example, this reduces the thermal load to be applied to a cold source such as an air conditioner for an air-cooled condenser, a cooling tower or a chiller for a water-cooled condenser, etc., thereby providing energy-saving operation. Furthermore such an arrangement exhibits stable dehumidification performance even in a case in which the load of the compressed air to be dehumidified is great. In addition, such an arrangement is capable of preventing occurrence of dew condensation in a sure manner at the outlet pipe via which the dehumidified compressed air is externally discharged, even in a case in which the temperature of the compressed air is low.
  • FIG. 1 is a circuit diagram which shows a refrigeration circuit and a compressed air circuit of a refrigeration air dryer according to an embodiment of the present invention.
  • FIG. 2 is a circuit diagram which shows a refrigeration circuit and a compressed air circuit of a conventional refrigeration air dryer.
  • FIG. 1 shows an embodiment of a refrigeration air dryer according to the present invention.
  • the refrigeration air dryer according to the embodiment includes a refrigerant system and an air system in which several components are the same as those in the conventional refrigeration air dryer shown in FIG. 2 . Accordingly, in FIG. 1 , the same components as those in FIG. 2 are denoted by the same reference numerals.
  • the major difference between the embodiment and the conventional refrigeration air dryer shown in FIG. 2 is that the embodiment employs a first reheater 18 and a second reheater 19 in order to reduce electric power consumption while maintaining the stable operation of the refrigeration air dryer.
  • the refrigerant system in the refrigeration air dryer shown in FIG. 1 includes a refrigerant compressor 10 , a condenser 11 which condenses a high-temperature refrigerant which has been compressed by the refrigerant compressor 10 and has been transmitted from a high-temperature refrigerant pipe 22 via the second reheater 19 , an expansion valve 12 which decompresses, by adiabatic expansion, the refrigerant thus condensed by the condenser 11 so as to lower the temperature of the refrigerant, and a cooler 13 which again cools the air, which has been preliminarily cooled by the first reheater 18 in the air system, using the low-temperature refrigerant transmitted from the expansion valve 12 .
  • the refrigerant system is configured such that the refrigerant transmitted from the cooler 13 is returned to the refrigerant compressor 10 via a return refrigerant pipe 20 .
  • expansion valve 12 has been illustrated as an example of the decompressing mechanism. Also, capillary tubes or the like may be employed instead of the expansion valve, for example.
  • the air system of the refrigeration air dryer includes: an air inlet 20 which allows warm and moist primary air (rated temperature of 40° C.), which is to be dehumidified, to flow into the air system; the first reheater 18 which preliminarily cools the primary air and raises the temperature of the dehumidified air by exchanging heat between the primary air input via the air inlet 20 and the low-temperature dehumidified air transmitted from the cooler 13 ; the cooler 13 which again cools, using the refrigerant, the air thus preliminarily cooled by the first reheater 18 so as to condense the moisture; a drain separator 16 which performs drain separation processing for the air thus cooled again by the cooler 13 , and transmits the air in a low-temperature (approximately 10° C.) and dehumidified state to the first reheater 18 ; and the second reheater 19 which again raises the temperature of the humidified air, of which the temperature has been raised by exchanging heat with the
  • cooler 13 and the second reheater 19 are connected to both the refrigerant system and the air system, and functionally connect the refrigerant system and the air system.
  • the drain separator 16 which performs the drain separation processing, includes a drain valve 15 which externally discharges resultant water drops.
  • the reheater 19 is provided between the refrigerant compressor 10 and the condenser 11 , and is a component which again raises the temperature of the dehumidified air by exchanging heat between the high-temperature refrigerant compressed by the refrigerant compressor 10 and the dehumidified air, of which the temperature has been preliminarily raised by the first reheater 18 and which has been transmitted via the air pipe 28 , using the difference in temperature therebetween.
  • the second reheater 19 includes the high-temperature refrigerant pipe 22 via which the refrigerant, of which the temperature has been raised by the refrigerant compressor 10 , is transmitted to the second reheater, and the outlet pipe 21 via which the dehumidified air having a temperature raised by exchanging heat with this refrigerant is externally discharged.
  • the temperatures of the refrigerant and the compressed air at each component in the refrigerant system and the air system in the refrigeration air dryer are almost the same as those in the conventional refrigeration air dryer shown in FIG. 2 , except that the temperature of the compressed air (secondary air) at the outlet pipe 21 is approximately 45° C. However, there is a great difference in the stability of these temperatures therebetween.
  • the high-temperature refrigerant pipe 22 that connects the refrigerant compressor 10 and the second reheater 19 and the low-temperature refrigerant pipe 23 that connects the expansion valve 12 and the cooler 13 communicate with each other via a bypass refrigerant pipe 25 including a volume adjusting valve 17 which provides an adjustable opening.
  • the bypass refrigerant pipe 25 is provided in order to maintain the temperature of the low-temperature refrigerant such that it does not become equal to or smaller than a predetermined temperature, by mixing a portion of the high-temperature refrigerant from the refrigerant compressor 10 into the low-temperature refrigerant in the low-temperature refrigerant pipe 23 , bypassing the second reheater 19 , the condenser 11 , and the expansion valve 12 , by instructing the volume adjusting valve 17 to provide a suitable opening, thereby preventing the moisture included in the moist air, which flows from the first reheater 18 to the cooler 13 via the air pipe 24 , from freezing due to excessive reduction in the temperature of the refrigerant flowing from the expansion valve 12 to the cooler 13 via the low-temperature refrigerant pipe 23 , in a case in which the load of the cooler 13 has become small.
  • the bypass refrigerant pipe 25 is a component which adjusts the flow rate of the refrigerant flowing through the second reheater 19 , the condenser 11 , and the expansion valve 12 .
  • By adjusting the flow rate such an arrangement is capable of preventing a situation in which the temperature of the dehumidified air is excessively raised in the reheating step at the reheater 19 .
  • bypass refrigerant pipe 25 may be connected to the high-temperature refrigerant pipe 22 and the return refrigerant pipe 26 which connects the cooler 13 and the refrigerant compressor 10 .
  • the flow rate of the refrigerant flowing through the cooler 13 is reduced, thereby providing the same advantage as that provided by the above-described arrangement, i.e., the advantage of preventing the moisture included in the air, which is cooled by the cooler 13 , from freezing.
  • the refrigeration air dryer shown in FIG. 1 provides the heat quantity Q 3 which is smaller by the heat quantity Q 4 than that in the conventional refrigeration air dryer shown in FIG. 2 . This also reduces the heat quantity Q 2 , thereby reducing energy consumption.
  • the heat discharged from the refrigeration air dryer is processed by temperature management equipment such as an air conditioner, cooling tower, chiller, etc.
  • the refrigeration air dryer having such a configuration reduces energy consumption as described above, thereby exhibiting high humidification performance with small electric power consumption.
  • such an arrangement is capable of reducing the heat exchanger duty of the condenser (heat quantity discharged from the condenser), thereby reducing the thermal load to be applied to a cold source (air conditioner for an air-cooled condenser, cooling tower or chiller for a water-cooled condenser).
  • a cold source air conditioner for an air-cooled condenser, cooling tower or chiller for a water-cooled condenser.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Oil, Petroleum & Natural Gas (AREA)
  • General Chemical & Material Sciences (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Power Engineering (AREA)
  • Drying Of Gases (AREA)
  • Drying Of Solid Materials (AREA)
US12/557,750 2008-10-03 2009-09-11 Refrigeration air dryer Abandoned US20100083683A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2008258839A JP2010088971A (ja) 2008-10-03 2008-10-03 冷凍式エアドライヤ
JP2008-258839 2008-10-03

Publications (1)

Publication Number Publication Date
US20100083683A1 true US20100083683A1 (en) 2010-04-08

Family

ID=42074696

Family Applications (1)

Application Number Title Priority Date Filing Date
US12/557,750 Abandoned US20100083683A1 (en) 2008-10-03 2009-09-11 Refrigeration air dryer

Country Status (6)

Country Link
US (1) US20100083683A1 (ko)
JP (1) JP2010088971A (ko)
KR (1) KR20100038138A (ko)
CN (1) CN101711940A (ko)
DE (1) DE102009043737A1 (ko)
TW (1) TW201020482A (ko)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102818332A (zh) * 2012-08-02 2012-12-12 青岛海信日立空调系统有限公司 控制多联机空调系统中辅助电加热的方法及装置
WO2015168755A1 (en) * 2014-05-09 2015-11-12 Atlas Copco Airpower, Naamloze Vennootschap Method and device for cool-drying a gas with circulating cooling liquid with bypass line
BE1021844B1 (nl) * 2014-05-09 2016-01-22 Atlas Copco Airpower, Naamloze Vennootschap Inrichting en werkwijze voor het koeldrogen van een gas
CN106765770A (zh) * 2016-12-30 2017-05-31 东南大学 一种冷凝与溶液分级除湿的高效新风空调处理装置及方法
CN109780809A (zh) * 2018-12-20 2019-05-21 青岛海尔股份有限公司 冰箱及冰箱的控湿方法
WO2020232084A1 (en) * 2019-05-14 2020-11-19 Kyllburg Technologies, LLC Refrigerator moisture removal system

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2012245501A (ja) * 2011-05-31 2012-12-13 Orion Machinery Co Ltd 圧縮空気除湿装置
CN103040086B (zh) * 2012-12-28 2015-04-22 广州晟启能源设备有限公司 除湿热泵组件及烟草除湿热泵烘烤装置
EP3714962B1 (de) * 2019-03-29 2021-12-15 Kaeser Kompressoren SE Druckluftstation
EP3714963B1 (de) * 2019-03-29 2021-12-22 Kaeser Kompressoren SE Druckluftstation
CN110345044A (zh) * 2019-07-05 2019-10-18 华北电力大学 一种双地下储气室带储热循环的压缩二氧化碳储能系统
WO2021117199A1 (ja) * 2019-12-12 2021-06-17 三菱電機株式会社 除湿装置
KR102373185B1 (ko) * 2021-04-13 2022-03-11 김경희 에너지 절약형 듀플렉스 에어드라이어

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5146364Y2 (ko) * 1972-02-10 1976-11-09
JPS56144895U (ko) * 1980-03-31 1981-10-31
JPS6195424U (ko) * 1984-11-26 1986-06-19

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102818332A (zh) * 2012-08-02 2012-12-12 青岛海信日立空调系统有限公司 控制多联机空调系统中辅助电加热的方法及装置
WO2015168755A1 (en) * 2014-05-09 2015-11-12 Atlas Copco Airpower, Naamloze Vennootschap Method and device for cool-drying a gas with circulating cooling liquid with bypass line
BE1021844B1 (nl) * 2014-05-09 2016-01-22 Atlas Copco Airpower, Naamloze Vennootschap Inrichting en werkwijze voor het koeldrogen van een gas
US10232309B2 (en) 2014-05-09 2019-03-19 Atlas Copco Airpower, Naamloze Vennootschap Method and device for cool-drying a gas with circulating cooling liquid with bypass line
CN106765770A (zh) * 2016-12-30 2017-05-31 东南大学 一种冷凝与溶液分级除湿的高效新风空调处理装置及方法
CN109780809A (zh) * 2018-12-20 2019-05-21 青岛海尔股份有限公司 冰箱及冰箱的控湿方法
WO2020232084A1 (en) * 2019-05-14 2020-11-19 Kyllburg Technologies, LLC Refrigerator moisture removal system

Also Published As

Publication number Publication date
TW201020482A (en) 2010-06-01
JP2010088971A (ja) 2010-04-22
KR20100038138A (ko) 2010-04-13
CN101711940A (zh) 2010-05-26
DE102009043737A1 (de) 2010-06-17

Similar Documents

Publication Publication Date Title
US20100083683A1 (en) Refrigeration air dryer
US8915092B2 (en) Heat pump system having a pre-processing module
US10920760B2 (en) Air compressor having an oil separator, an oil cooler, first and second evaporators, and wherein intake air and the oil are simultaneously cooled in the first and second evaporators
US20100107674A1 (en) Refrigeration air dryer
US6425257B1 (en) Air conditioner
CN106322811A (zh) 车用空调换热系统和车辆
CN207471687U (zh) 空调系统及具有该空调系统的空调器
CN114801645A (zh) 一种无ptc加热器的氢能汽车不结霜热泵系统及热管理方法
US8037709B2 (en) Heat pump with pressure reducer
KR20050072299A (ko) 냉난방 공기조화시스템
JP2009210213A (ja) 鉄道車両用空調装置
WO2012055268A1 (zh) 温控处理系统和方法
CN105352234B (zh) 一种自适应相变冷凝空调系统及其实现方法
KR100528292B1 (ko) 히트펌프식 공기조화기
CN111156615B (zh) 基于双级压缩机系统的控制器散热系统及其控制方法
JPH05157372A (ja) 空気調和機の電気品箱冷却装置
KR101560825B1 (ko) 공기조화시스템
JP2004177064A (ja) 空気調和機
WO2021063272A1 (zh) 热管理系统
CN108397830A (zh) 一种新型全效多模式节能空调系统
KR100512037B1 (ko) 공기조화기
KR101579117B1 (ko) 핫가스 제상과 히트펌프를 병행한 시스템
CN112146302B (zh) 一种蒸发冷热泵机组
CN220689213U (zh) 一种升温除湿空气处理一体机
JP2007147133A (ja) 空気調和装置

Legal Events

Date Code Title Description
AS Assignment

Owner name: SMC CORPORATION,JAPAN

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:AONO, HIDEAKI;REEL/FRAME:023219/0875

Effective date: 20090826

STCB Information on status: application discontinuation

Free format text: EXPRESSLY ABANDONED -- DURING EXAMINATION