WO2011070779A1 - 車両用空調装置 - Google Patents

車両用空調装置 Download PDF

Info

Publication number
WO2011070779A1
WO2011070779A1 PCT/JP2010/007151 JP2010007151W WO2011070779A1 WO 2011070779 A1 WO2011070779 A1 WO 2011070779A1 JP 2010007151 W JP2010007151 W JP 2010007151W WO 2011070779 A1 WO2011070779 A1 WO 2011070779A1
Authority
WO
WIPO (PCT)
Prior art keywords
pressure refrigerant
low
refrigerant
storage unit
cold storage
Prior art date
Application number
PCT/JP2010/007151
Other languages
English (en)
French (fr)
Inventor
伸彦 藤井
Original Assignee
サンデン株式会社
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
Priority claimed from JP2009279188A external-priority patent/JP2011020667A/ja
Application filed by サンデン株式会社 filed Critical サンデン株式会社
Priority to EP10835702.1A priority Critical patent/EP2511113A4/en
Priority to CN201080055879XA priority patent/CN102639347A/zh
Priority to US13/516,330 priority patent/US20120312050A1/en
Publication of WO2011070779A1 publication Critical patent/WO2011070779A1/ja

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
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating [HVAC] devices
    • B60H1/00321—Heat exchangers for air-conditioning devices
    • B60H1/00342—Heat exchangers for air-conditioning devices of the liquid-liquid type
    • 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
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/05—Compression system with heat exchange between particular parts of the system
    • F25B2400/053—Compression system with heat exchange between particular parts of the system between the storage receiver and another part of the system
    • 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
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/24—Storage receiver heat

Definitions

  • the present invention relates to a vehicle air conditioner provided with a refrigerant circuit having a compressor, a condenser, a decompressor, and an evaporator.
  • this type of vehicle air conditioner includes a refrigerant circuit having a compressor, a condenser, a decompressor, and an evaporator, and cools the vehicle interior by driving the compressor using a vehicle engine as a drive source. It has become.
  • an internal heat exchanger for exchanging heat between the high-pressure refrigerant on the downstream side of the condenser and the low-pressure refrigerant on the downstream side of the evaporator is provided in the refrigerant circuit so as to improve the cooling capacity. Things are known.
  • the compressor circuit is also stopped simultaneously with the stop of the engine. Since the refrigerant does not circulate, the cooling cannot be continued. Therefore, in order to continue cooling while the compressor is stopped, the refrigerant flow path on the downstream side of the evaporator of the refrigerant circuit has a cold storage material inside, and cools the cold storage material with the low-pressure refrigerant during operation of the compressor, A cold storage heat exchanger is provided that cools the low-pressure refrigerant with the cold storage material when the compressor is stopped, and the refrigerant is liquefied with the cold storage material when the compressor is stopped. After the compressor stops, the high-pressure side and the low-pressure side of the refrigerant circuit It is known that the cooling until a predetermined time can be continued by delaying the time until the pressure becomes uniform (see, for example, Patent Document 1).
  • the vehicle air conditioner has a large number of parts constituting the refrigerant circuit, such as an internal heat exchanger and a cold storage heat exchanger, and has a large number of parts and a large number of assembly steps. Become.
  • An object of the present invention is to provide a vehicle air conditioner that can reduce an occupied space and reduce the number of parts and the number of assembling steps by integrating a plurality of parts constituting a refrigerant circuit. It is in.
  • the present invention provides a vehicle air conditioner including a refrigerant circuit having a compressor, a condenser, a decompressor, and an evaporator, and high-pressure refrigerant on the downstream side of the condenser circulates in the refrigerant circuit.
  • the low-pressure refrigerant in the low-pressure refrigerant flow path is cooled by the low-pressure refrigerant in the low-pressure refrigerant flow path when the compressor is driven, and the cold storage material in the cool storage material accommodation unit is cooled when the compressor is stopped.
  • a cold storage internal heat exchanger is provided to cool the battery.
  • the function as the internal heat exchanger and the function as the cold storage heat exchanger can be achieved by one component of the cold storage internal heat exchanger, so that the space occupied by the refrigerant circuit is reduced and the number of parts and the number of assembly steps are reduced. Can be reduced.
  • the refrigerant circuit diagram of the vehicle air conditioner which shows one Embodiment of this invention Side cross-sectional view of cold storage internal heat exchanger AA 'sectional view of FIG. BB 'sectional view of FIG.
  • 1 to 4 show an embodiment of the present invention.
  • the vehicle air conditioner of the present invention is applied to a vehicle including an idling stop mechanism that detects that the vehicle has stopped due to a signal waiting or the like and stops the engine, and includes the refrigerant circuit 1 shown in FIG. .
  • the refrigerant circuit 1 includes a compressor 2, a condenser 3, an expansion valve 4 serving as a decompressor, and an evaporator 5, a high-pressure refrigerant on the downstream side of the condenser 3, and a low-pressure on the downstream side of the evaporator 5.
  • a cold storage internal heat exchanger 10 for exchanging heat between the high pressure refrigerant on the downstream side of the condenser 3 and the low pressure refrigerant on the downstream side of the evaporator 5 and the cold storage material is connected.
  • the compressor 2 used here is driven by using the engine of the vehicle as a drive source. When the engine is stopped by the idling stop mechanism, the drive is stopped simultaneously.
  • the evaporator 5 is provided inside the air conditioning unit in the vehicle interior, and the air exchanged with the refrigerant in the evaporator 5 is supplied to the vehicle interior by the blower 5a.
  • the compressor 2, the condenser 3, the expansion valve 4, and the cool storage internal heat exchanger 10 are provided inside the engine room outside the passenger compartment.
  • HFC134a is used as a refrigerant.
  • the cold storage internal heat exchanger 10 is formed in a cylindrical shape extending in the horizontal direction, and an internal heat exchange unit 20 that exchanges heat between the high-pressure refrigerant downstream of the condenser 3 and the low-pressure refrigerant downstream of the evaporator 5 at one end.
  • the cold storage heat exchanger 30 for exchanging heat between the high pressure refrigerant downstream of the condenser 3 and the low pressure refrigerant downstream of the evaporator 5 and the cold storage material is provided on the other end side.
  • the internal heat exchanging unit 20 includes a first tubular member 21, a second tubular member 22 provided in a lower portion of the first tubular member 21, and one ends of the first tubular member 21 and the second tubular member. And a partition plate 24 that is provided at the other end of the first cylindrical member 21 and the second cylindrical member 22 and partitions the internal heat exchange unit 20 and the cold storage heat exchange unit 30. Has been.
  • the cold storage heat exchange unit 30 includes a third cylindrical member 31 in which a cold storage material is accommodated, a fourth cylindrical member 32 provided in an upper part of the third cylindrical member 31, and a third cylindrical member 31.
  • a fifth cylindrical member 33 provided in the lower part of the inside, a third cylindrical member 31, a fourth cylindrical member 32, a partition plate 24 provided at one end of the fifth cylindrical member 33, and a third cylindrical shape.
  • the second closing plate 34 is configured to close the other end of the member 31, the fourth cylindrical member 32, and the fifth cylindrical member 33.
  • the first closing plate 23 located at the upper part of one end of the first cylindrical member 21 is provided with a low-pressure refrigerant outlet 23 a, and the first closing plate 23 located at the lower part of one end of the second cylindrical member 22 is provided in the first closing plate 23.
  • a high-pressure refrigerant inlet 23b is provided.
  • the partition plate 24 located at the upper end of the other end of the first cylindrical member 21 and the upper end of the one end of the fourth cylindrical member 32 is provided with a first communication hole 24 a and the second cylindrical member 22.
  • a second communication hole 24 b is provided in the partition plate 24 located at the lower portion of the other end of the first cylindrical member 33 and at one end of the fifth cylindrical member 33.
  • the second closing plate 34 positioned at the upper part of the other end of the fourth cylindrical member 32 is provided with a low-pressure refrigerant inlet 34 a, and the second closing plate 34 positioned at the other end of the fifth cylindrical member 33. Is provided with a high-pressure refrigerant outlet 34b. That is, the high-pressure refrigerant storage unit 11 in which the high-pressure refrigerant flowing out of the condenser 3 flows and the predetermined amount of high-pressure refrigerant can be stored is provided in the second cylindrical member 22 and the fifth cylindrical member 33.
  • a low-pressure refrigerant storage section 12 is provided in the first cylindrical member 21 and the fourth cylindrical member 32, in which the low-pressure refrigerant flowing out of the evaporator 5 is circulated and a predetermined amount of low-pressure refrigerant can be stored.
  • a regenerator material accommodating portion 13 is provided inside the member 31 .
  • the coolant and water for engine cooling are accommodated as a cool storage material.
  • the compressor 2 when the vehicle travels, the compressor 2 is driven, and the refrigerant discharged from the compressor 2 radiates and liquefies in the condenser 3, and is stored in the cold storage internal heat exchanger. 10 high-pressure refrigerant storage units 11 are distributed. Further, the refrigerant flowing out of the high pressure refrigerant storage unit 11 of the cold storage internal heat exchanger 10 is depressurized in the expansion valve 4 and absorbs heat in the evaporator 5 to evaporate, and passes through the low pressure refrigerant storage unit 12 of the cold storage internal heat exchanger 10. After being distributed, it is sucked into the compressor 2.
  • the regenerator material accommodated in the regenerator material accommodation unit 13 of the regenerator internal heat exchanger 10 is cooled by the low-pressure refrigerant flowing through the low-pressure refrigerant storage unit 12 via the fourth cylindrical member 32. .
  • the refrigerant flowing through the high-pressure refrigerant storage unit 11 of the cold-storage internal heat exchanger 10 is cooled by exchanging heat with the refrigerant flowing through the low-pressure refrigerant storage unit 12 via the second cylindrical member 22, thereby being supercooled.
  • the cooling is further performed by exchanging heat with the regenerator material accommodated in the regenerator material accommodation unit 13 via the fifth cylindrical member 33, the degree of supercooling is increased.
  • the refrigerant flows from the high pressure side to the low pressure side until the pressure in the refrigerant circuit 1 becomes uniform. Since the low-pressure refrigerant in the low-pressure refrigerant storage unit 12 of the heat exchanger 10 is cooled and liquefied by the regenerator material in the regenerator storage unit 13, the increase in the pressure on the low-pressure side of the refrigerant circuit 1 becomes slow, and the refrigerant circuit 1 The time until the pressure becomes uniform becomes longer. As a result, even when the driving of the compressor 2 is stopped, the cooling of the passenger compartment can be continued while the refrigerant is circulating in the refrigerant circuit 1.
  • coolant storage part 12 of the cool storage internal heat exchanger 10 in the state which the drive of the compressor 2 has stopped is cooled and liquefied by the cool storage material of the cool storage material accommodating part 13, and a low pressure refrigerant
  • the overflowing liquid refrigerant flows into the first cylindrical member 21 of the low-pressure side storage unit 12 and passes through the second cylindrical member 22.
  • the liquid refrigerant Since it is heated and vaporized by the refrigerant in the high-pressure refrigerant storage unit 12, the liquid refrigerant does not flow out from the refrigerant outlet 23 a provided in the upper part of the first cylindrical member 21 of the low-pressure refrigerant storage unit 12.
  • the high-pressure refrigerant storage unit 11 in which the high-pressure refrigerant on the downstream side of the condenser 3 circulates in the refrigerant circuit 1 and the low-pressure refrigerant on the downstream side of the evaporator 5.
  • It has a low-pressure refrigerant storage unit 12 that circulates and a heat storage material storage unit 13 in which a heat storage material is stored, and performs heat exchange between the high-pressure refrigerant in the high-pressure refrigerant storage unit 11 and the low-pressure refrigerant in the low-pressure refrigerant storage unit 12, and compression
  • the cold storage material in the cold storage material storage unit 13 is cooled by the low pressure refrigerant in the low pressure refrigerant storage unit 12, and the low pressure refrigerant in the low pressure refrigerant storage unit 12 is cooled by the cold storage material in the cold storage material storage unit 13 when the compressor 2 is stopped.
  • the functions of the internal heat exchanger and the cold-storage heat exchanger can be achieved by a single component of the cold storage internal heat exchanger 10, and the space occupied by the refrigerant circuit 1 can be reduced. And the number of parts and It is possible to achieve a reduction of only with man-hours.
  • the high-pressure refrigerant in the high-pressure refrigerant storage unit 11 after heat exchange with the low-pressure refrigerant in the low-pressure refrigerant storage unit 12 is cooled by the cold storage material in the cold storage material storage unit 13. Is brought into a supercooled state by heat exchange with the refrigerant in the low-pressure refrigerant storage unit 12, and then the degree of supercooling of the high-pressure refrigerant can be increased by heat exchange with the cold storage material in the cool storage material storage unit 13. Supercooling can be performed reliably.
  • a low-pressure refrigerant storage unit 12 that can store a predetermined amount of low-pressure refrigerant while the low-pressure refrigerant on the downstream side of the evaporator 5 circulates in the cold storage internal heat exchanger 10, and a refrigerant outlet 21 a of the low-pressure refrigerant storage unit 12 is provided. Is provided in the upper part of the first cylindrical member 21, so that the low-pressure refrigerant cooled and liquefied by the cold storage material can be prevented from flowing out of the low-pressure refrigerant storage unit 12, and a separate accumulator is provided in the refrigerant circuit 1. It becomes possible to prevent the liquid compression of the compressor 2 without.
  • coolant of the downstream of the condenser 3 distribute
  • coolants was provided
  • coolant liquefied in the condenser 3 is provided.
  • the refrigerant can be temporarily stored in the high-pressure refrigerant storage unit 11, and the refrigerant can be reliably supplied to the evaporator 5 when the cooling load changes without providing a separate liquid receiver in the refrigerant circuit 1.
  • the high-pressure refrigerant in the high-pressure refrigerant storage unit 11 after heat exchange with the low-pressure refrigerant in the low-pressure refrigerant storage unit 12 is cooled by the cold storage material in the cold storage material storage unit 13, the liquefied refrigerant is stored in the high-pressure refrigerant storage unit 11. Therefore, even if the internal capacity of the second cylindrical member 22 is increased, the high-pressure refrigerant can be sufficiently subcooled, and the accumulator function and the internal heat exchange function can be reliably obtained.
  • the present invention is widely applicable to air conditioners equipped with a refrigerant circuit having a compressor, a condenser, a decompressor, and an evaporator.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Air-Conditioning For Vehicles (AREA)

Abstract

【課題】冷媒回路を構成する複数の部品を一体構成とすることにより、占有スペースを小さくすると共に部品点数及び組み付け工数の低減を図ることのできる車両空調装置を提供する。 【解決手段】　冷媒回路１に、凝縮器３の下流側の高圧冷媒が流通する高圧冷媒貯蔵部１１と、蒸発器５の下流側の低圧冷媒が流通する低圧冷媒貯蔵部１２と、蓄熱材が収容された蓄熱材収容部１３とを有し、高圧冷媒貯蔵部１１の高圧冷媒と低圧冷媒貯蔵部１２の低圧冷媒とを熱交換するとともに、圧縮機２の駆動時に低圧冷媒貯蔵部１２の低圧冷媒によって蓄冷材収容部１３の蓄冷材を冷却し、低圧冷媒貯蔵部１２の低圧冷媒と熱交換した後の高圧冷媒貯蔵部１１の高圧冷媒を蓄冷材収容部１３の蓄冷材によって冷却し、圧縮機２の停止時に蓄冷材収容部１３の蓄冷材によって低圧冷媒貯蔵部１２の低圧冷媒を冷却する蓄冷内部熱交換器１０を設けた。

Description

車両用空調装置
　本発明は、圧縮機、凝縮器、減圧器、蒸発器を有する冷媒回路を備えた車両用空調装置に関するものである。
　従来、この種の車両用空調装置では、圧縮機、凝縮器、減圧器、蒸発器を有する冷媒回路を備え、車両のエンジンを駆動源として圧縮機を駆動することにより車室内を冷房するようになっている。
　前記車両用空調装置では、凝縮器の下流側の高圧冷媒と蒸発器の下流側の低圧冷媒とを熱交換するための内部熱交換器を冷媒回路に設け、冷房能力の向上を図るようにしたものが知られている。
　ところで、信号待ち等による停車を検知してエンジンを停止するアイドリングストップ機構を備えた車両に対して前記空調装置を適用する場合には、エンジンの停止と同時に圧縮機の駆動も停止して冷媒回路に冷媒が流通しなくなるため、冷房を継続することができない。そこで、圧縮機の停止中に冷房を継続するため、冷媒回路の蒸発器の下流側の冷媒流路に、内部に蓄冷材を有し、圧縮機の運転時に低圧冷媒によって蓄冷材を冷却し、圧縮機の停止時に蓄冷材によって低圧冷媒を冷却する蓄冷熱交換器を設け、圧縮機の停止時に蓄冷材によって冷媒を液化し、圧縮機が停止してから冷媒回路の高圧側と低圧側との圧力が均一になるまでの時間を遅らせることにより、所定時間の冷房の継続が可能となるようにしたものが知られている（例えば、特許文献１参照）。
特開２００７－１４８５号公報
　前記車両空調装置では、内部熱交換器や蓄冷熱交換器等、冷媒回路を構成する部品を多数有しており、部品点数が多く、組み付け工数が多くなるため、占有スペースが大きく製造コストが高くなる。
　本発明の目的とするところは、冷媒回路を構成する複数の部品を一体構成とすることにより、占有スペースを小さくすると共に部品点数及び組み付け工数の低減を図ることのできる車両空調装置を提供することにある。
　本発明は前記目的を達成するために、圧縮機、凝縮器、減圧器、蒸発器を有する冷媒回路を備えた車両用空調装置において、前記冷媒回路に、凝縮器の下流側の高圧冷媒が流通する高圧冷媒流路と、蒸発器の下流側の低圧冷媒が流通する低圧冷媒流路と、蓄冷材が収容された蓄冷材収容部とを有し、高圧冷媒流路の高圧冷媒と低圧冷媒流路の低圧冷媒とを熱交換するとともに、圧縮機の駆動時に低圧冷媒流路の低圧冷媒によって蓄冷材収容部の蓄冷材を冷却し、圧縮機の停止時に蓄冷材によって低圧冷媒流路の低圧冷媒を冷却する蓄冷内部熱交換器を設けている。
　これにより、凝縮器の下流側の高圧冷媒の過冷却度が大きくなるとともに、圧縮機の停 止時に蒸発器の下流側の低圧冷媒が液化されることから、蓄冷内部熱交換器の一部品によって内部熱交換器としての機能及び蓄冷熱交換器としての機能が果たされる。
　本発明によれば、蓄冷内部熱交換器の一部品によって内部熱交換器としての機能及び蓄冷熱交換機としての機能を果たすことができるので、冷媒回路の占有スペースを小さくすると共に部品点数及び組み付け工数の低減を図ることが可能となる。
本発明の一実施形態を示す車両用空調装置の冷媒回路図 蓄冷内部熱交換器の側面断面図 図３のＡ－Ａ′断面図 図３のＢ－Ｂ′断面図
　図１乃至図４は本発明の一実施形態を示すものである。
　本発明の車両用空調装置は、信号待ち等で停車したことを検知してエンジンを停止するアイドリングストップ機構を備えた車両に適用されるものであり、図１に示す冷媒回路１を備えている。
　冷媒回路１は、圧縮機２、凝縮器３、減圧器としての膨張弁４及び蒸発器５を有する周知の冷凍サイクルに、凝縮器３の下流側の高圧冷媒と蒸発器５の下流側の低圧冷媒とを熱交換するとともに、凝縮器３の下流側の高圧冷媒及び蒸発器５の下流側の低圧冷媒と蓄冷材とを熱交換するための蓄冷内部熱交換器１０が接続されたものである。ここで用いられる圧縮機２は、車両のエンジンを駆動源として駆動するようになっており、アイドリングストップ機構によってエンジンが停止した場合に、同時に駆動が停止するものである。また、この車両用空調装置は、蒸発器５が車室内の空調ユニットの内部に設けられ、蒸発器５において冷媒と熱交換した空気が送風機５ａによって車室内に供給されるようになっている。また、圧縮機２、凝縮器３、膨張弁４及び蓄冷内部熱交換器１０は、車室外のエンジンルームの内部に設けられている。また、冷媒回路１には、冷媒としてＨＦＣ１３４ａが用いられる。
　蓄冷内部熱交換器１０は、水平方向に延びる円筒形状に形成され、一端側に凝縮器３の下流側の高圧冷媒と蒸発器５の下流側の低圧冷媒とを熱交換する内部熱交換部２０が設けられ、他端側に凝縮器３の下流側の高圧冷媒及び蒸発器５の下流側の低圧冷媒と蓄冷材を熱交換する蓄冷熱交換部３０が設けられている。
　内部熱交換部２０は、第１筒状部材２１と、第１筒状部材２１内の下部に設けられた第２筒状部材２２と、第１筒状部材２１及び第２筒状部材の一端を閉鎖する第１閉鎖板２３と、第１筒状部材２１及び第２筒状部材２２の他端に設けられ、内部熱交換部２０と蓄冷熱交換部３０とを仕切る仕切板２４とから構成されている。
　蓄冷熱交換部３０は、内部に蓄冷材が収容された第３筒状部材３１と、第３筒状部材３１内の上部に設けられた第４筒状部材３２と、第３筒状部材３１内の下部に設けられた第５筒状部材３３と、第３筒状部材３１、第４筒状部材３２及び第５筒状部材３３の一端に設けられた仕切板２４と、第３筒状部材３１、第４筒状部材３２及び第５筒状部材３３の他端を閉鎖する第２閉鎖板３４とから構成されている。
　第１筒状部材２１の一端の上部に位置する第１閉鎖板２３には、低圧冷媒流出口２３ａ が設けられ、第２筒状部材２２の一端の下部に位置する第１閉鎖板２３には、高圧冷媒流入口２３ｂが設けられている。また、第１筒状部材２１の他端の上部、且つ、第４筒状部材３２の一端の上部に位置する仕切板２４には、第１連通孔２４ａが設けられ、第２筒状部材２２の他端の下部、且つ、第５筒状部材３３の一端に位置する仕切板２４には、第２連通孔２４ｂが設けられている。更に、第４筒状部材３２の他端の上部に位置する第２閉鎖板３４には、低圧冷媒流入口３４ａが設けられ、第５筒状部材３３の他端に位置する第２閉鎖板３４には、高圧冷媒流出口３４ｂが設けられている。即ち、第２筒状部材２２内及び第５筒状部材３３内に、凝縮器３から流出した高圧冷媒が流通すると共に所定量の高圧冷媒が貯蔵可能な高圧冷媒貯蔵部１１が設けられ、第１筒状部材２１内及び第４筒状部材３２内に、蒸発器５から流出した低圧冷媒が流通すると共に所定量の低圧冷媒が貯蔵可能な低圧冷媒貯蔵部１２が設けられ、第３筒状部材３１内に、蓄冷材収容部１３が設けられている。また、蓄冷材収容部１３内には、蓄冷材としてエンジン冷却用のクーラントや水が収容されている。
　以上のように構成された車両用空調装置において、車両の走行時には、圧縮機２が駆動され、圧縮機２から吐出された冷媒は、凝縮器３において放熱して液化し、蓄冷内部熱交換器１０の高圧冷媒貯蔵部１１を流通する。また、蓄冷内部熱交換器１０の高圧冷媒貯蔵部１１から流出した冷媒は、膨張弁４において減圧されて蒸発器５において吸熱して蒸発し、蓄冷内部熱交換器１０の低圧冷媒貯蔵部１２を流通した後、圧縮機２に吸入される。
　前記車両の走行時において、蓄冷内部熱交換器１０の蓄冷材収容部１３に収容された蓄冷材は、第４筒状部材３２を介して低圧冷媒貯蔵部１２を流通する低圧冷媒によって冷却される。蓄冷内部熱交換器１０の高圧冷媒貯蔵部１１を流通する冷媒は、第２筒状部材２２を介して低圧冷媒貯蔵部１２を流通する冷媒と熱交換して冷却されることにより過冷却の状態となり、第５筒状部材３３を介して蓄冷材収容部１３に収容された蓄冷材と更に熱交換することにより冷却されるため、過冷却度が大きくなる。また、蓄冷内部熱交換器１０の高圧冷媒貯蔵部１１である第２筒状部材２２内には、凝縮器３において液化した冷媒が一時的に貯えられるため、冷房負荷に応じて冷媒が蒸発器５に供給される。
　また、信号待ち等の停車を検知してエンジンが停止し、圧縮機２の駆動が停止すると、冷媒回路１内の圧力が均一となるまで高圧側から低圧側に冷媒が流入するが、蓄冷内部熱交換器１０の低圧冷媒貯蔵部１２の低圧冷媒は、蓄冷材収容部１３の蓄冷材によって冷却されて液化するため、冷媒回路１の低圧側の圧力の上昇が遅くなり、冷媒回路１内の圧力が均一となるまでの時間が長くなる。これにより、圧縮機２の駆動が停止した場合にも、冷媒回路１内を冷媒が流通している間は、車室内の冷房の継続が可能となる。
　また、圧縮機２の駆動が停止している状態で、蓄冷内部熱交換器１０の低圧冷媒貯蔵部１２を流通する冷媒は、蓄冷材収容部１３の蓄冷材によって冷却されて液化し、低圧冷媒貯蔵部１２の第４筒状部材３２内に溜まる。低圧冷媒貯蔵部１２の第４筒状部材３２から液冷媒が溢れると、溢れた液冷媒は、低圧側貯蔵部１２の第１筒状部材２１内に流れ、第２筒状部材２２を介して高圧冷媒貯蔵部１２の冷媒によって加熱されて気化するため、低圧冷媒貯蔵部１２の第１筒状部材２１の上部に設けられた冷媒流出口２３ａから液冷媒が流出することはない。
　このように、本実施形態の車両用空調装置によれば、冷媒回路１に、凝縮器３の下流側の高圧冷媒が流通する高圧冷媒貯蔵部１１と、蒸発器５の下流側の低圧冷媒が流通する低圧冷媒貯蔵部１２と、蓄熱材が収容された蓄熱材収容部１３とを有し、高圧冷媒貯蔵部１１の高圧冷媒と低圧冷媒貯蔵部１２の低圧冷媒とを熱交換するとともに、圧縮機２の駆動時に低圧冷媒貯蔵部１２の低圧冷媒によって蓄冷材収容部１３の蓄冷材を冷却し、圧縮機２の停止時に蓄冷材収容部１３の蓄冷材によって低圧冷媒貯蔵部１２の低圧冷媒を冷却する蓄冷内部熱交換器１０を設けたので、蓄冷内部熱交換器１０の一部品によって内部熱交換器の機能及び蓄冷熱交換器の機能を果たすことができ、冷媒回路１の占有スペースを小さくすると共に部品点数及び組み付け工数の低減を図ることが可能となる。
　また、圧縮機２の駆動時に、低圧冷媒貯蔵部１２の低圧冷媒と熱交換した後の高圧冷媒貯蔵部１１の高圧冷媒を蓄冷材収容部１３の蓄冷材によって冷却するようにしたので、高圧冷媒を低圧冷媒貯蔵部１２の冷媒との熱交換によって過冷却状態とした後、更に蓄冷材収容部１３の蓄冷材との熱交換によって高圧冷媒の過冷却度を大きくすることができ、高圧冷媒の過冷却を確実に行うことができる。
　更に、蓄冷内部熱交換器１０に、蒸発器５の下流側の低圧冷媒が流通すると共に所定量の低圧冷媒を貯蔵可能な低圧冷媒貯蔵部１２を設け、低圧冷媒貯蔵部１２の冷媒流出口２１ａを、第１筒状部材２１の上部に設けたので、蓄冷材によって冷却されて液化した低圧冷媒の低圧冷媒貯蔵部１２外への流出を防止することができ、冷媒回路１に別途アキュムレータを設けることなく圧縮機２の液圧縮を防止することが可能となる。
　また、蓄冷内部熱交換器１０に、凝縮器３の下流側の高圧冷媒が流通すると共に所定量の高圧冷媒を貯蔵可能な高圧冷媒貯蔵部１１を設けたので、凝縮器３において液化した冷媒を高圧冷媒貯蔵部１１に一時的に貯えることができ、冷媒回路１に別途受液器を設けることなく冷房負荷が変化する場合に確実に冷媒を蒸発器５に供給することが可能となる。
　この場合、低圧冷媒貯蔵部１２の低圧冷媒と熱交換した後の高圧冷媒貯蔵部１１の高圧冷媒が蓄冷材収容部１３の蓄冷材によって冷却されるため、液化した冷媒を高圧冷媒貯蔵部１１内に貯えるために第２筒状部材２２の内部容量を大きくしても、高圧冷媒の過冷却を十分に行うことができ、アキュムレータ機能と内部熱交換機能とを確実に得ることができる。
　本発明は、圧縮機、凝縮器、減圧器、蒸発器を有する冷媒回路を備えた空調装置に広く利用可能である。
　１…冷媒回路、２…圧縮機、３…凝縮器、４…膨張弁、５…蒸発器、１０…蓄冷内部熱交換器、１１…高圧冷媒貯蔵部、１２…低圧冷媒貯蔵部、１３…蓄冷材収容部、２０…内部熱交換部、２１…第１筒状部材、２２…第２筒状部材、３０…蓄冷熱交換部、３１…第３筒状部材、３２…第４筒状部材、３３…第５筒状部材。

Claims (4)

  1. 　圧縮機、凝縮器、減圧器、蒸発器を有する冷媒回路を備えた車両用空調装置において、
    　前記冷媒回路に、凝縮器の下流側の高圧冷媒が流通する高圧冷媒流路と、蒸発器の下流側の低圧冷媒が流通する低圧冷媒流路と、蓄冷材が収容された蓄冷材収容部とを有し、高圧冷媒流路の高圧冷媒と低圧冷媒流路の低圧冷媒とを熱交換するとともに、圧縮機の駆動時に低圧冷媒流路の低圧冷媒によって蓄冷材収容部の蓄冷材を冷却し、圧縮機の停止時に蓄冷材によって低圧冷媒流路の低圧冷媒を冷却する蓄冷内部熱交換器を設けた
    ことを特徴とする車両用空調装置。
  2. 　前記蓄冷内部熱交換器を、圧縮機の駆動時に低圧冷媒流路の低圧冷媒と熱交換した後の高圧冷媒流路の高圧冷媒を蓄冷材によって冷却するように構成した
    ことを特徴とする請求項１記載の車両用空調装置。
  3. 　前記蓄冷内部熱交換器の低圧冷媒流路として、蒸発器の下流側の低圧冷媒が流通すると共に所定量の低圧冷媒を貯蔵可能な低圧冷媒貯蔵部を設け、
    　低圧冷媒貯蔵部の低圧冷媒の流出口を、低圧冷媒貯蔵部の上部に設けた
    ことを特徴とする請求項１または２記載の車両用空調装置。
  4. 　前記蓄冷内部熱交換器の高圧冷媒流路として、凝縮器の下流側の高圧冷媒が流通すると共に所定量の高圧冷媒を貯蔵可能な高圧冷媒貯蔵部を設けたことを特徴とする請求項１、２または３記載の車両用空調装置。
PCT/JP2010/007151 2009-06-17 2010-12-08 車両用空調装置 WO2011070779A1 (ja)

Priority Applications (3)

Application Number Priority Date Filing Date Title
EP10835702.1A EP2511113A4 (en) 2009-12-09 2010-12-08 AIR CONDITIONING FOR VEHICLES
CN201080055879XA CN102639347A (zh) 2009-12-09 2010-12-08 车辆用空调装置
US13/516,330 US20120312050A1 (en) 2009-06-17 2010-12-13 Vehicular air conditioner

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2009-279188 2009-12-09
JP2009279188A JP2011020667A (ja) 2009-06-17 2009-12-09 車両用空調装置

Publications (1)

Publication Number Publication Date
WO2011070779A1 true WO2011070779A1 (ja) 2011-06-16

Family

ID=44145891

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2010/007151 WO2011070779A1 (ja) 2009-06-17 2010-12-08 車両用空調装置

Country Status (3)

Country Link
EP (1) EP2511113A4 (ja)
CN (1) CN102639347A (ja)
WO (1) WO2011070779A1 (ja)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102645059A (zh) * 2011-12-12 2012-08-22 浙江吉利汽车研究院有限公司 汽车空调系统

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS58174659U (ja) * 1982-05-17 1983-11-22 三菱重工業株式会社 空気調和装置
JPH0539960A (ja) * 1991-08-06 1993-02-19 Tabai Espec Corp 冷凍装置
JPH08320157A (ja) * 1995-05-26 1996-12-03 Daikin Ind Ltd 冷凍装置
JP2007001485A (ja) 2005-06-24 2007-01-11 Denso Corp 車両用冷凍サイクル装置
JP2009154804A (ja) * 2007-12-27 2009-07-16 Calsonic Kansei Corp 車両用空調装置

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2504437B2 (ja) * 1987-01-30 1996-06-05 株式会社東芝 空調機
US20040089439A1 (en) * 2002-11-07 2004-05-13 Treverton Andrew Clare Tube-to-tube heat exchanger assembly
CN1590929A (zh) * 2003-08-25 2005-03-09 乐金电子(天津)电器有限公司 空调机的贮液罐
US6964178B2 (en) * 2004-02-27 2005-11-15 Denso Corporation Air conditioning system for vehicle
FR2930020B1 (fr) * 2008-04-10 2014-09-19 Valeo Systemes Thermiques Echangeur interne comportant un moyen de stockage thermique et boucle incorporant un tel echangeur.

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS58174659U (ja) * 1982-05-17 1983-11-22 三菱重工業株式会社 空気調和装置
JPH0539960A (ja) * 1991-08-06 1993-02-19 Tabai Espec Corp 冷凍装置
JPH08320157A (ja) * 1995-05-26 1996-12-03 Daikin Ind Ltd 冷凍装置
JP2007001485A (ja) 2005-06-24 2007-01-11 Denso Corp 車両用冷凍サイクル装置
JP2009154804A (ja) * 2007-12-27 2009-07-16 Calsonic Kansei Corp 車両用空調装置

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of EP2511113A4 *

Also Published As

Publication number Publication date
EP2511113A1 (en) 2012-10-17
CN102639347A (zh) 2012-08-15
EP2511113A4 (en) 2013-05-15

Similar Documents

Publication Publication Date Title
JP7516987B2 (ja) 接続モジュール
US20200353790A1 (en) Vehicle-mounted temperature controller
WO2011087001A1 (ja) 車両用空調システム
US20120291478A1 (en) Condenser for vehicle and air conditioning system for vehicle
JP2021156567A (ja) 冷凍サイクル装置
RU2472643C1 (ru) Система для охлаждения и нагревания
US20140060102A1 (en) Mild ambient vehicular heat pump system
US20140096560A1 (en) Cooling system for vehicle
US9440512B2 (en) Air conditioning system for vehicle
WO2014073151A1 (ja) 冷凍サイクル装置
US20070283703A1 (en) Air conditioning unit for vehicles and method of operating the same
JP7176405B2 (ja) 温度調整装置
WO2021100409A1 (ja) 冷凍サイクル装置
CN110466309B (zh) 车辆的冷却和加热系统
US20220194167A1 (en) Connection module
JP7516761B2 (ja) 冷凍サイクル装置
EP2592366A2 (en) Non-azeotropic mixed refrigerant cycle and refrigerator equipped therewith
WO2023026869A1 (ja) 圧縮機モジュール
JP4508006B2 (ja) 車両用冷凍サイクル装置
JP2019027690A (ja) 複合型熱交換器
WO2011070779A1 (ja) 車両用空調装置
JP2011020667A (ja) 車両用空調装置
JP2017172948A (ja) 熱交換ユニットおよび車両用空調装置
JP5388896B2 (ja) 車両用空調装置
KR101734281B1 (ko) 차량용 컨덴서

Legal Events

Date Code Title Description
WWE Wipo information: entry into national phase

Ref document number: 201080055879.X

Country of ref document: CN

121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 10835702

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: DE

WWE Wipo information: entry into national phase

Ref document number: 2010835702

Country of ref document: EP

WWE Wipo information: entry into national phase

Ref document number: 13516330

Country of ref document: US