WO2013084418A1 - Cycle de réfrigération du type à éjecteur - Google Patents

Cycle de réfrigération du type à éjecteur Download PDF

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Publication number
WO2013084418A1
WO2013084418A1 PCT/JP2012/007317 JP2012007317W WO2013084418A1 WO 2013084418 A1 WO2013084418 A1 WO 2013084418A1 JP 2012007317 W JP2012007317 W JP 2012007317W WO 2013084418 A1 WO2013084418 A1 WO 2013084418A1
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WO
WIPO (PCT)
Prior art keywords
refrigerant
evaporator
ejector
distributor
passage
Prior art date
Application number
PCT/JP2012/007317
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English (en)
Japanese (ja)
Inventor
大介 櫻井
押谷　洋
大石　繁次
高野　義昭
Original Assignee
株式会社デンソー
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Publication of WO2013084418A1 publication Critical patent/WO2013084418A1/fr

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    • 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
    • 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
    • F25B41/00—Fluid-circulation arrangements
    • 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
    • F25B5/00—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity
    • F25B5/04—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity arranged in series
    • 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
    • B60H1/32—Cooling devices
    • B60H2001/3286—Constructional features
    • B60H2001/3298—Ejector-type refrigerant circuits
    • 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
    • F25B2341/00—Details of ejectors not being used as compression device; Details of flow restrictors or expansion valves
    • F25B2341/001—Ejectors not being used as compression device
    • F25B2341/0011—Ejectors with the cooled primary flow at reduced or low pressure

Definitions

  • This disclosure relates to an ejector refrigeration cycle having an ejector.
  • Patent Document 1 to Patent Document 7 disclose an ejector-type refrigeration cycle apparatus.
  • a branch portion is provided between the radiator and the evaporator of the refrigeration cycle apparatus.
  • One of the branched refrigerants is supplied to the nozzle of the ejector.
  • the other branched refrigerant is supplied to the suction port of the ejector through the evaporator. That is, one of the branched refrigerants is used for power, and the other branched refrigerant is used for evaporation.
  • Patent Document 2 to Patent Document 7 propose to add an internal heat exchange function for exchanging heat between the refrigerant before evaporation and the refrigerant before compression.
  • JP 2006-258396 A Japanese Patent Laid-Open No. 2007-3166 Japanese Patent Laid-Open No. 2007-40586 JP 2007-212121 A JP 2008-8572 A JP 2008-51397 A JP 2010-266198 A
  • the state of the refrigerant toward the nozzle and the refrigerant toward the evaporator and the suction port are in the same state, for example, the same gas-liquid two-phase state.
  • inhaled by a compressor becomes high with an internal heat exchanger, the flow volume of the whole refrigerating cycle may fall, and the fall of a flow volume may reduce the performance of an ejector.
  • the present disclosure has been made in view of the above problems, and an object of the present disclosure is to provide an ejector-type refrigeration cycle that can extract the performance of the ejector while utilizing the effect of the internal heat exchanger. .
  • Another object of the present disclosure is to provide an ejector refrigeration cycle capable of increasing the latent heat available in the evaporator and increasing the flow rate supplied to the ejector.
  • the ejector-type refrigeration cycle of the present disclosure adjusts the refrigerant flow rate so that the compressor that sucks in, compresses and discharges the refrigerant, and controls the degree of superheat of the sucked refrigerant to the compressor to a predetermined value.
  • a first decompressor that decompresses the high-pressure refrigerant to an intermediate pressure
  • a distributor that distributes the refrigerant decompressed by the first decompressor
  • a liquid phase that is connected to the distributor and distributed by the distributor.
  • An ejector having a suction port for sucking the refrigerant from the downstream end of the second passage by the flow of the injected refrigerant, and a diffuser portion for decelerating and boosting the refrigerant injected from the nozzle portion and the refrigerant sucked from the suction port ing.
  • an internal heat exchanger for exchanging heat between the refrigerant flowing between the distributor and the second decompressor and the
  • the flow rate of the refrigerant supplied from the distributor to the nozzle portion increases as the flow rate to the suction side evaporator decreases.
  • the ejector can exhibit high performance. Therefore, the heat absorption capability that can be used in the suction-side evaporator can be increased by the internal heat exchanger, and the ejector can exhibit high performance.
  • the flow rate supplied from the distributor to the second passage exhibits a predetermined endothermic capacity in the suction side evaporator including an increase in the endothermic capacity of the suction side evaporator due to heat exchange in the internal heat exchanger.
  • the suction side flow rate may be used, and the flow rate supplied from the distributor to the first passage may be a nozzle side flow rate obtained by subtracting the suction side flow rate from the amount of refrigerant flowing into the distributor.
  • the heat absorption capacity of the suction side evaporator is increased by heat exchange in the internal heat exchanger.
  • the flow rate of the second passage is set to a flow rate that exhibits a predetermined heat absorption capability in the suction-side evaporator, including this increase.
  • the flow rate in the first passage is set to the nozzle side flow rate. As a result, the flow rate supplied to the nozzle portion is relatively increased.
  • the flow rate of the second passage and the flow rate of the first passage are set according to the configuration of the passages.
  • the flow rate of the second passage and the flow rate of the first passage are, for example, the configuration of the distributor, the pressure loss of the second decompressor, the pressure loss of the suction side evaporator, the suction force of the ejector, the pressure loss of the nozzle portion, etc. It depends on the factors.
  • the predetermined endothermic ability exhibited in the suction side evaporator may be an endothermic ability in which the degree of superheat of the refrigerant at the outlet of the suction side evaporator is lower than a predetermined value.
  • a flow rate at which the degree of superheat of the refrigerant at the outlet of the suction side evaporator is less than a predetermined value is supplied to the second passage.
  • a discharge-side evaporator that is provided between the diffuser portion and the internal heat exchanger and evaporates the refrigerant may be provided. According to this configuration, the refrigerant can be evaporated also downstream of the diffuser portion.
  • An integrated unit comprising at least two of a plurality of low-pressure components including a first decompressor, a distributor, an ejector, a second decompressor, a suction side evaporator, a discharge side evaporator, and an internal heat exchanger You may comprise as. According to this configuration, at least two low-pressure components are integrally configured as a unit. As a result, handling of a plurality of parts becomes easy.
  • the unit may include a distributor and an internal heat exchanger. According to this configuration, the distributor and the internal heat exchanger can be handled as a unit.
  • the unit may include a discharge side evaporator.
  • the internal heat exchanger and the discharge-side evaporator can be handled as a unit.
  • the unit may further include a second decompressor.
  • the second decompressor can be handled as a unit.
  • the unit may further include an ejector.
  • the ejector can be further handled as a unit.
  • the unit may further include a suction side evaporator. According to this configuration, the components including the suction side evaporator can be further reduced in size.
  • FIG. 3 is a ph diagram showing a refrigerant state in the ejector refrigeration cycle of the first embodiment. It is a graph which shows the performance of the ejector type refrigerating cycle of a 1st embodiment. It is a typical perspective view showing an evaporator unit used for an ejector type refrigerating cycle of a 2nd embodiment of this indication. It is a typical exploded view of the evaporator unit of a 2nd embodiment. It is a fragmentary sectional view of the evaporator unit of a 2nd embodiment.
  • an ejector-type refrigeration cycle 10 has a plurality of components.
  • the components are compressor 11, radiator 12, decompressor 13 (first decompressor), distributor 16, ejector 14, first evaporator 15 (discharge side evaporator), decompressor 17 (second decompressor).
  • a second evaporator 18 (suction side evaporator), and an internal heat exchanger 40.
  • the plurality of components are connected by a plurality of pipes so as to constitute the refrigeration cycle shown in FIG.
  • the refrigeration cycle 10 is mounted on a vehicle and used for air conditioning in the passenger compartment.
  • the compressor 11 sucks the refrigerant and compresses it, and then discharges the high-pressure refrigerant.
  • the compressor 11 is rotationally driven by a vehicle travel engine (not shown) via an electromagnetic clutch 11a and a belt.
  • the compressor 11 may be an electric compressor.
  • the heat radiator 12 is connected to the discharge side of the compressor 11.
  • the radiator 12 can be used as an indoor unit or an outdoor unit. When used as an outdoor unit, the radiator 12 provides heat exchange between the high-pressure refrigerant discharged from the compressor 11 and the vehicle exterior air.
  • the radiator 12 cools the high-pressure refrigerant.
  • a cooling fan that blows air to the radiator 12 may be provided.
  • the refrigeration cycle 10 uses a refrigerant whose high pressure, that is, the refrigerant pressure flowing out of the compressor 11 does not exceed the critical pressure, such as a refrigerant of chlorofluorocarbon and HC.
  • the refrigeration cycle 10 constitutes a vapor compression subcritical cycle. Therefore, the radiator 12 functions as a condenser that condenses the refrigerant.
  • the decompressor 13 is connected to the outlet side of the radiator 12.
  • the decompressor 13 is an example of a decompressing unit that decompresses the high-pressure liquid refrigerant discharged from the radiator 12.
  • the decompressor 13 supplies an intermediate-pressure refrigerant in a gas-liquid two-phase state to the downstream side.
  • the decompressor 13 is also called a main decompressor in the refrigeration cycle 10.
  • the decompressor 13 is a temperature type decompressor.
  • the decompressor 13 has a temperature sensing part 13 a disposed in the suction side passage of the compressor 11.
  • the decompressor 13 adjusts the refrigerant flow rate so as to control the superheat degree of the refrigerant sucked into the compressor 11 to a predetermined value, and depressurizes the high-pressure refrigerant to an intermediate pressure.
  • the decompressor 13 detects the degree of superheat of the compressor suction side refrigerant based on the temperature and pressure of the suction side refrigerant of the compressor 11.
  • the decompressor 13 adjusts the decompression amount so that the degree of superheat of the compressor suction side refrigerant becomes a predetermined value set in advance.
  • This predetermined value is set so that the degree of superheat of the refrigerant at the outlet of the evaporator 15 does not reach such a high value that the temperature distribution of the evaporator 15 is deteriorated.
  • the predetermined value is set so that the gas-liquid two-phase refrigerant evaporates in almost the entire evaporator 15.
  • the predetermined value is set such that the degree of refrigerant superheating downstream of the internal heat exchanger 40, which will be described later, does not adversely affect the compressor 11.
  • the refrigerant flow rate is adjusted according to the pressure reduction amount of the pressure reducer 13.
  • a pressure reducing valve may be used as the pressure reducing device 13, and the amount of pressure reduction is adjusted by adjusting the valve opening.
  • the ejector 14 is connected to the outlet side of the decompressor 13 via the distributor 16.
  • the ejector 14 is an example of a decompression unit that further decompresses the intermediate-pressure refrigerant.
  • the ejector 14 is also an example of a refrigerant transport means that generates a refrigerant flow by the suction action of the refrigerant flow ejected at high speed.
  • the ejector 14 generates a refrigerant flow in the second passage 51 (branch passage) in the refrigeration cycle 10.
  • the ejector 14 can also be called a momentum transport pump.
  • the ejector 14 includes a nozzle portion 14a, a suction port 14b, a mixing portion 14c, and a diffuser portion 14d.
  • the first passage 50 (first passage) in the refrigeration cycle 10 is connected to the nozzle portion 14a, and the refrigerant supplied therefrom is injected.
  • the nozzle portion 14a further expands the intermediate pressure refrigerant under reduced pressure by narrowing the refrigerant passage area.
  • the ejector 14 generates an entrainment action, that is, a suction force, by the refrigerant flow injected from the outlet of the nozzle portion 14a.
  • a part of the refrigerant flow circulating in the refrigeration cycle 10 is supplied to the nozzle portion 14a.
  • the first refrigerant flow (main flow) of the refrigerant that is, the refrigerant flowing through the first passage 50 is supplied to the nozzle portion 14a.
  • the ejector 14 includes a suction port 14b that communicates with the vicinity of the jet port of the nozzle portion 14a.
  • the suction port 14b is connected to the downstream end of the second passage 51 configured in the refrigeration cycle 10, and the refrigerant flowing through the second passage 51 by the flow of the refrigerant injected from the nozzle portion 14a passes through the suction port 14b. Sucked.
  • a second refrigerant flow (branch flow) of the refrigerant, that is, the refrigerant flowing through the second passage 51 is supplied to the suction port 14b.
  • the mixing part 14c is provided in the refrigerant
  • the mixing unit 14c mixes the high-speed refrigerant flow from the nozzle unit 14a and the refrigerant sucked from the refrigerant suction port 14b.
  • a diffuser portion 14d forming a pressure increasing portion is disposed on the refrigerant flow downstream side of the mixing portion 14c.
  • the diffuser part 14d decelerates and pressurizes the refrigerant injected from the nozzle part 14a and the refrigerant sucked from the suction port 14b.
  • the diffuser portion 14d has a shape that gradually increases the passage area of the refrigerant toward the downstream side of the refrigerant flow.
  • the diffuser part 14d decelerates the refrigerant flow to increase the refrigerant pressure, that is, converts the velocity energy of the refrigerant into pressure energy.
  • the downstream end portion of the diffuser portion 14 d is an outlet portion of the ejector 14.
  • the two evaporators 15 and 18 each evaporate the refrigerant and cause the refrigerant to absorb heat.
  • the first evaporator 15 is disposed on the upstream side of the second evaporator 18 with respect to the air flow F ⁇ b> 1 that is the object of temperature adjustment.
  • the first evaporator 15 is also called an upwind evaporator disposed upstream of the air flow F1, that is, on the upwind side.
  • the second evaporator 18 is also called a leeward evaporator disposed on the downstream side of the air flow F1, that is, on the leeward side.
  • the two evaporators 15 and 18 are configured and arranged to act on a common cooling load.
  • the two evaporators 15 and 18 are accommodated in an air conditioning case (not shown).
  • the air conditioning case has an air conditioning duct, and air to be cooled is blown into the air conditioning duct by an electric blower 19 as indicated by an arrow F1.
  • the two evaporators 15 and 18 cool the air blown by the blower 19.
  • the cold air cooled by the two evaporators 15 and 18 is sent into a common cooling target space. As a result, the common space to be cooled is cooled by the two evaporators 15 and 18.
  • the first evaporator 15 is connected to the downstream side of the diffuser portion 14d of the ejector 14.
  • the first evaporator 15 is also referred to as a downstream evaporator provided on the downstream side of the diffuser portion 14d or a discharge side evaporator.
  • the second evaporator 18 is disposed in the second passage 51 connected to the suction port 14b of the ejector 14.
  • the second evaporator 18 is also called an upstream evaporator disposed on the upstream side of the suction port 14b of the ejector 14 or a suction side evaporator.
  • the gas-phase refrigerant exiting from the second evaporator 18 is sucked into the ejector 14 through the suction port 14b.
  • the distributor 16 is connected to the outlet side of the decompressor 13.
  • the distributor 16 distributes the refrigerant flowing out of the decompressor 13 into a plurality of passages.
  • the distributor 16 is connected to the outlet side of the decompressor 13 so that the refrigerant flows into the inlet 16a, the first outlet 16b connected to the inlet of the nozzle portion 14a via the first passage 50, and the second A second outlet 16 c connected to the passage 51 is provided.
  • the refrigerant flows out from the second outlet 16c toward the suction port 14b.
  • the distributor 16 distributes the gas-liquid two-phase refrigerant into the first passage 50 and the second passage 51.
  • the distributor 16 distributes the refrigerant into the first passage 50 toward the nozzle portion 14a and the second passage 51 toward the suction port 14b. That is, when the refrigerant having the flow rate G (inflow amount) flows into the distributor 16 from the decompressor 13, the distributor 16 supplies the refrigerant with the flow rate Gn (nozzle side flow rate) to the first passage 50 and supplies the refrigerant to the second passage 51. A refrigerant having a flow rate Ge (suction side flow rate) is supplied. The distributor 16 adjusts the ratio of the flow rate Gn and the flow rate Ge to a predetermined ratio.
  • the distributor 16 adjusts the gas-liquid component of the refrigerant so as to give a difference between the gas-liquid ratio of the refrigerant toward the first passage 50 and the gas-liquid ratio of the refrigerant toward the second passage 51.
  • the distributor 16 adjusts the refrigerant going to the first passage 50 to a refrigerant having a relatively large amount of gas phase components.
  • the distributor 16 adjusts the refrigerant going to the second passage 51 to a refrigerant having a relatively large liquid phase component.
  • the distributor 16 supplies a refrigerant having a larger gas phase than the liquid phase to the first passage 50 toward the nozzle portion 14a, and supplies a refrigerant having a larger liquid phase than the gas phase to the second passage 51 toward the suction port 14b.
  • the distributor 16 adjusts the gas-liquid component of the refrigerant so that the gas phase component of the refrigerant going to the first passage 50 is larger than the gas phase component of the refrigerant going to the second passage 51.
  • the distributor 16 supplies the first passage 50 with a gas-liquid two-phase refrigerant that is mostly a gas-phase refrigerant.
  • the distributor 16 supplies the second passage 51 with a gas-liquid two-phase refrigerant that is mostly a liquid-phase refrigerant.
  • the distributor 16 can be provided by a centrifuge, for example.
  • the decompressor 17 is disposed in the second passage 51 and is connected to the upstream side of the second evaporator 18. Therefore, the second evaporator 18 is provided between the decompressor 17 and the suction port 14b.
  • the decompressor 13 decompresses the refrigerant from high pressure to intermediate pressure, and the decompressor 17 decompresses the refrigerant from intermediate pressure to low pressure.
  • the decompressor 17 is also called a sub decompressor in the refrigeration cycle 10.
  • the decompressor 17 is a decompression unit that is connected to the inlet side of the second evaporator 18 and adjusts the refrigerant flow rate to the second evaporator 18.
  • the decompressor 17 can be provided by a restriction mechanism such as a capillary tube or a restriction passage.
  • the internal heat exchanger 40 includes an upstream passage 41 through which the refrigerant before evaporation flows and a downstream passage 42 through which the refrigerant after evaporation flows.
  • the internal heat exchanger 40 is configured to provide heat exchange between the refrigerant in the upstream passage 41 and the refrigerant in the downstream passage 42.
  • the upstream passage 41 is disposed in the second passage 51 and connected to the upstream side of the second pressure reducer 17. That is, the upstream passage 41 is disposed between the second outlet 16 c and the decompressor 17.
  • the downstream passage 42 is located on the downstream side of the ejector 14, and the downstream passage 42 is located between the ejector 14 and the suction side of the compressor 11.
  • the downstream passage 42 is connected to the downstream side of the first evaporator 15, and the first evaporator 15 is provided between the diffuser portion 14 d and the internal heat exchanger 40.
  • the internal heat exchanger 40 cools the intermediate pressure refrigerant flowing in the upstream passage 41 by the low pressure refrigerant flowing in the downstream passage 42.
  • the internal heat exchanger 40 exchanges heat between the refrigerant flowing between the distributor 16 and the decompressor 17 and the refrigerant downstream of the first evaporator 15. In typical operating conditions, the intermediate pressure refrigerant is subcooled in the upstream passage 41.
  • FIG. 2 shows the relationship between the refrigerant pressure P and the enthalpy H in a typical operating state.
  • a curve PH1 indicates the characteristics of the refrigerant used in the refrigeration cycle 10
  • a curve PH2 indicates the characteristics of the refrigerant having a large latent heat.
  • a refrigerant having a small latent heat indicated by the curve PH1 is used.
  • the evaporators 15 and 18 can exhibit a sufficiently large heat absorption capability.
  • the refrigerant is compressed by the operation of the compressor 11.
  • the high-temperature refrigerant dissipates heat and condenses.
  • the high-pressure refrigerant flowing out of the radiator 12 is decompressed by the decompressor 13.
  • the amount of decompression is adjusted so that the degree of superheat of the outlet refrigerant of the first evaporator 15 becomes a predetermined value.
  • the intermediate pressure refrigerant is distributed by the distributor 16.
  • the refrigerant is divided into a first refrigerant flow from the first outlet 16b toward the nozzle portion 14a and a second refrigerant flow from the second outlet 16c toward the decompressor 17.
  • the refrigerant of the first refrigerant flow is decompressed and expanded by the nozzle portion 14a.
  • the pressure energy of the refrigerant is converted into velocity energy at the nozzle portion 14a, and the refrigerant is ejected at a high speed from the outlet of the nozzle portion 14a. Due to the pressure drop caused by the high-speed refrigerant flow, the refrigerant of the second refrigerant flow that has passed through the second evaporator 18 is sucked from the suction port 14b.
  • the second refrigerant flow is supercooled by the internal heat exchanger 40.
  • the internal heat exchanger 40 gives the enthalpy hx that can be used in the second evaporator 18 to the intermediate pressure refrigerant.
  • the supercooled refrigerant is decompressed by the decompressor 17 and becomes a low-pressure refrigerant.
  • the decompressed refrigerant flows through the second evaporator 18.
  • the low-temperature low-pressure refrigerant absorbs heat from the blown air after passing through the first evaporator 15 and evaporates.
  • the second evaporator 18 as shown in FIG.
  • the enthalpy of the refrigerant changes by enthalpy hde by absorbing heat from the air.
  • enthalpy hde is used during endotherm.
  • the flow rate Ge of the refrigerant flowing through the second evaporator 18 is set so that the degree of superheat of the refrigerant does not become excessively large.
  • the degree of superheat of the outlet refrigerant is set such that the second evaporator 18 does not cause a large distribution in the temperature of the cooled air.
  • the degree of superheating of the outlet refrigerant is set to, for example, 5 ° C. or less, desirably 3 ° C. or less, so that the refrigerant evaporates in almost the entire area of the second evaporator 18. Thereafter, the refrigerant is sucked into the ejector 14 from the suction port 14b.
  • the refrigerant ejected from the nozzle part 14a and the refrigerant sucked from the suction port 14b are mixed in the mixing part 14c and then flow into the diffuser part 14d.
  • the refrigerant pressure rises because the velocity energy of the refrigerant is converted into pressure energy by expanding the passage area.
  • the pressure rise by the ejector 14 is the pressure Pej shown in FIG.
  • the refrigerant that has flowed out of the diffuser section 14d flows through the first evaporator 15.
  • the low-temperature low-pressure refrigerant absorbs heat from the blown air and evaporates.
  • the refrigerant exiting the first evaporator 15 is superheated by the internal heat exchanger 40.
  • the internal heat exchanger 40 gives enthalpy hx to the low-pressure refrigerant.
  • the decompressor 13 adjusts the flow rate G so that the degree of superheat of the refrigerant at the outlet of the internal heat exchanger 40 becomes a predetermined value. Therefore, the superheat degree of the refrigerant sucked into the compressor 11 is prevented from becoming excessively high.
  • the flow rate G is also adjusted at the outlet of the first evaporator 15 so that the degree of superheat of the refrigerant does not become excessively large.
  • the decompressor 13 adjusts the flow rate G so as not to cause a large distribution in the temperature of the air cooled by the first evaporator 18.
  • the flow rate G is adjusted so that the refrigerant evaporates in almost the entire area of the first evaporator 15. Thereafter, the refrigerant is sucked into the compressor 11 and compressed again.
  • the refrigerant evaporation pressure of the second evaporator 18 can be made lower than the refrigerant evaporation pressure of the first evaporator 15.
  • the first evaporator 15 having a high refrigerant evaporation temperature is arranged on the upstream side in the air flow direction F1
  • the second evaporator 18 having a low refrigerant evaporation temperature is arranged on the downstream side in the air flow direction F1.
  • the temperature difference between the refrigerant evaporation temperature and the blown air in the first evaporator 15 and the temperature difference between the refrigerant evaporation temperature and the blown air in the second evaporator 18 are both maintained large, and the heat absorption performance is improved. Can be increased. Further, the driving power of the compressor 11 can be reduced by increasing the suction refrigerant pressure of the compressor 11 by the pressure increasing action in the diffuser portion 14d.
  • the improvement in performance by the ejector 14 and the improvement in the heat absorption performance by the internal heat exchanger 40 are conspicuous in improving the overall heat absorption capability of the refrigeration cycle 10. Contributing.
  • the enthalpy hde available in the second evaporator 18 is increased by heat exchange in the internal heat exchanger 40.
  • the flow rate Ge of the second passage 51 with respect to the flow rate Gn of the first passage 50 can be reduced.
  • the predetermined endothermic performance can be obtained in the second evaporator 18 even if the flow rate Ge is reduced.
  • a decrease in the flow rate Ge results in an increase in the flow rate Gn.
  • the increase in the flow rate Gn increases the flow rate passing through the nozzle portion 14a.
  • the distributor 16 distributes the refrigerant containing more gas phase than the liquid phase to the nozzle portion 14a. As a result, the recovered energy in the ejector 14 increases.
  • the robustness of the refrigeration cycle 10 is improved and the operation can be continued without causing failure. That is, according to this embodiment, the heat absorption capability of the refrigeration cycle 10 can be improved. If the refrigerant flow rate decreases, it is also conceivable that the region of the superheated refrigerant in the downstream portion in the evaporators 15 and 18 becomes larger. However, the heat exchange in the internal heat exchanger 40 increases the enthalpy hde that can be used in the second evaporator 18, so the degree of superheat at the outlet of the second evaporator 18 can be reduced.
  • the degree of superheat at the outlet of the first evaporator 15 is reduced, a predetermined heat absorption capability can be obtained.
  • the temperature distribution on the surfaces of the evaporators 15 and 18 can be made uniform.
  • the uniform temperature distribution makes the distribution of the blowing temperature uniform at a low flow rate.
  • the flow rate Ge flowing through the second evaporator 18 can be reduced, pressure loss in the second evaporator 18 can be suppressed. The suppression of the pressure loss makes it possible to reliably flow the refrigerant through the second passage 51 even at a low flow rate. As a result, the endothermic performance at a low flow rate is improved.
  • the flow rate supplied from the distributor 16 to the second passage 51 includes the second evaporation including the increase in heat absorption capacity hx of the second evaporator 18 due to heat exchange in the internal heat exchanger 40.
  • the heat absorption capability of the second evaporator 18 is increased by heat exchange in the internal heat exchanger 40.
  • the flow rate of the second passage 51 is set to a flow rate at which a predetermined heat absorption capability is exhibited in the second evaporator 18 in consideration of this increase. That is, a smaller flow rate flows through the second passage 51 than when the increase is not taken into account.
  • the flow rate of the first passage 50 is set to the remaining flow rate Gn. As a result, the flow rate supplied to the nozzle portion 14a increases relatively.
  • the flow rate of the second passage 51 and the flow rate of the first passage 50 are set according to the configuration of the passages.
  • the flow rate of the second passage 51 and the flow rate of the first passage 50 are, for example, the configuration of the distributor 16, the pressure loss of the second decompressor 17, the pressure loss of the second evaporator 18, and the suction force of the ejector 14. It varies depending on factors such as pressure loss of the nozzle portion 14a.
  • the predetermined heat absorption capability exhibited in the second evaporator 18 is set so that the degree of superheat of the refrigerant at the outlet of the second evaporator 18 is below a predetermined value. According to this configuration, a flow rate at which the degree of superheat of the refrigerant at the outlet of the second evaporator 18 is less than a predetermined value is supplied to the second passage 51. As a result, since the gas-liquid two-phase refrigerant is evaporated in almost the entire second evaporator 18, the temperature distribution in the second evaporator 18 is kept small.
  • FIG. 3 shows the relationship between the performance of the ejector 14 and the amount of heat exchange in the internal heat exchanger 40.
  • the horizontal axis indicates the ratio Qx / Qe between the heat exchange amount Qx in the internal heat exchanger 40 and the heat absorption capability Qe in the evaporators 15 and 18.
  • shaft shows the flow volume G of the whole refrigerating cycle 10, and the flow volume Gn which flows into the nozzle part 14a.
  • the solid line indicates the flow rate Gn.
  • the broken line indicates the flow rate G.
  • the configuration of the internal heat exchanger 40 in other words, the heat exchange capacity in the internal heat exchanger 40 is effective for the entire evaporators 15 and 18 while fully drawing out the performance of the ejector 14. It is set so that it can be utilized.
  • the amount of heat exchange in the internal heat exchanger 40 can be set so that the temperature distribution in the evaporators 15 and 18 can be made uniform.
  • the flow rate Gn is increased. be able to.
  • the latent heat available in the second evaporator 18 increases due to the increase in the heat exchange amount Qx, and the flow rate Ge can be decreased. Therefore, the flow rate Ge necessary for obtaining a predetermined heat absorption capacity in the second evaporator 18 decreases as the heat exchange amount Qx increases. As a result, the flow rate Gn can be increased.
  • the increase in the flow rate Gn makes it possible to improve the performance of the ejector 14. In other words, the ejector 14 is set so that the performance is improved by an increase in the refrigerant containing more gas phase than the liquid phase supplied from the distributor 16. Specifically, the recovery amount of the expansion energy in the ejector 14 can be increased by increasing the flow rate Gn.
  • the increase in the amount of heat exchange Qx contributes to improving the performance of the ejector 14, but on the other hand, the overall capacity of the first evaporator 15 and the evaporators 15 and 18 is reduced. . Therefore, the heat exchange amount Qx is set so that both the performance of the ejector 14 and the capabilities of the evaporators 15 and 18 can be achieved.
  • the plurality of component parts have been described as independent parts. Alternatively, several parts can be integrated so that they can be handled as a unit.
  • FIG. 4 shows an evaporator unit 220 used in the ejector refrigeration cycle of the second embodiment.
  • FIG. 4 shows an evaporator unit 220 used in the ejector refrigeration cycle of the second embodiment.
  • FIG. 5 is an exploded view showing the configuration of the evaporator unit 220 and the flow path of the refrigerant.
  • each part will be described with names corresponding to the vertical direction and the horizontal direction in the drawing, but the arrangement state of the evaporator unit 220 is not limited to the illustrated example. .
  • the evaporator unit 220 includes an ejector 14, a first evaporator 15, a distributor 16, a second decompressor 17, a second evaporator 18, and an internal heat exchanger 40.
  • the evaporator unit 220 is configured as a unit that can be integrally handled by connecting these components.
  • the evaporator unit 220 is configured by integrally connecting a plurality of components by fixing means such as brazing, bolts, screws, and adhesion.
  • the evaporator unit 220 can also be called an evaporator unit for an ejector refrigeration cycle, an integrated unit for an ejector refrigeration cycle, or an evaporator unit with an ejector.
  • the two evaporators 15 and 18 are integrally formed.
  • a cylindrical ejector case 23 is disposed on the sides of the two evaporators 15 and 18.
  • the ejector 14 is accommodated in an ejector case 23.
  • the distributor 16 is integrally provided in the ejector 14 by being formed in the ejector case 23.
  • the ejector 14 is provided integrally with the evaporators 15 and 18 as a part of the evaporator unit 220.
  • the first evaporator 15 constitutes an upstream region of the air flow F1 in one evaporator structure
  • the second evaporator 18 constitutes a downstream region of the air flow F1 in one evaporator structure. Yes.
  • the basic configuration of the first evaporator 15 and the second evaporator 18 is the same.
  • the evaporators 15 and 18 include core portions 15a and 18a for heat exchange.
  • the core parts 15a and 18a are provided with a plurality of heat exchange tubes 21 extending in the vertical direction. Between the plurality of tubes 21, a passage through which the air to be cooled, which is a heat exchange medium, passes is formed. Fins 22 joined to the tubes 21 are disposed between the plurality of tubes 21.
  • the tubes 21 and the fins 22 are alternately stacked in the left-right direction of the core portions 15a and 18a.
  • Core portions 15 a and 18 a are formed by a laminated structure of the tube 21 and the fins 22.
  • the core portions 15 a and 18 a may be formed by a configuration of only the tube 21 that does not include the fins 22.
  • the evaporators 15 and 18 are provided with tank portions 15b, 15c, 18b and 18c extending in the left-right direction in the drawing at both ends in the vertical direction in the drawing.
  • the tank portions 15b, 15c, 18b, and 18c constitute independent refrigerant passage spaces, that is, tank spaces.
  • Tank portions 15b and 15c are arranged above and below the core portion 15a.
  • Tank portions 18b and 18c are arranged above and below the core portion 18a.
  • the tank portions 15 b and 15 c communicate with the upper and lower ends of the tube 21.
  • the tank portions 18 b and 18 c communicate with the upper and lower ends of the tube 21.
  • a partition plate 28 that divides the internal space of the upper tank portion 15b into a first space 26 and a second space 27 is disposed at a substantially central portion in the longitudinal direction inside the upper tank portion 15b.
  • a partition plate 31 that divides the internal space of the upper tank portion 18b into a first space 29 and a second space 30 is disposed at a substantially central portion in the longitudinal direction inside the upper tank portion 18b.
  • the refrigerant inlet 24 of the evaporator unit 220 is provided at one end portion of the upper tank portion 18b, that is, the left end portion in the drawing.
  • the refrigerant outlet 25 is provided at one end portion of the upper tank portion 15b, that is, the left end portion in the figure.
  • the refrigerant inlet 24 communicates with the inflow port 16a.
  • the refrigerant outlet 25 communicates with the upper tank portion 15b.
  • the tank portions 15b, 15c, 18b, and 18c serve to distribute the refrigerant to the plurality of tubes 21 of the corresponding core portions 15a and 18a and to collect the refrigerant from the plurality of tubes 21.
  • the second space 27 serves as a distribution tank that distributes the refrigerant to the first group of the plurality of tubes 21 belonging to the first evaporator 15.
  • the first space 26 serves as a collection tank that collects the refrigerant that has passed through the second group of the plurality of tubes 21 belonging to the first evaporator 15.
  • the lower tank portion 15c serves as a redistribution tank that collects the refrigerant from the first group of tubes and then redistributes the refrigerant to the second group of tubes.
  • the first space 29 serves as a distribution tank that distributes the refrigerant to the first group of the plurality of tubes 21 belonging to the second evaporator 18.
  • the second space 30 serves as a collection tank that collects the refrigerant that has passed through the second group of the plurality of tubes 21 belonging to the second evaporator 18.
  • the lower tank portion 18c serves as a redistribution tank that collects the refrigerant from the first group of tubes and then redistributes the refrigerant to the second group of tubes.
  • the ejector 14 and the distributor 16 are disposed on the upper side (TOP) of the upper tank portions 15b and 18b.
  • the ejector 14 includes a nozzle portion 14a, a suction portion 14b, a mixing portion 14c, and a diffuser portion 14d.
  • the ejector 14 has an elongated shape extending in the axial direction of the nozzle portion 14a.
  • the ejector 14 is disposed on the upper tank portions 15b and 18b so that the longitudinal direction thereof is parallel to the longitudinal direction of the tank portion.
  • the outlet of the ejector 14 opens into the internal space of the ejector case 23.
  • the internal space of the ejector case 23 communicates with the second space 27.
  • the suction port 14 b communicates with the second space 30.
  • the distributor 16 is arranged so as to be aligned with the ejector 14 along the longitudinal direction of the ejector 14.
  • the distributor 16 includes a cylindrical housing 16e.
  • the housing 16e is formed in a cylindrical shape extending in the axial direction of the nozzle portion 14a.
  • the housing 16e divides and forms a separation chamber 16d for rotating the refrigerant and separating it into a gas phase refrigerant and a liquid phase refrigerant.
  • the separation chamber 16d is a cylindrical space.
  • the housing 16e forms an inlet 16a for introducing the refrigerant into the separation chamber 16d, a first outlet 16b that opens to the separation chamber 16d, and a second outlet 16c that opens radially outward of the separation chamber 16d.
  • the inflow port 16a is provided at one end of the distributor 16, that is, the left end in the drawing.
  • the 1st outflow port 16b is provided in the other end part of the divider
  • the distributor 16 is disposed on the inlet side of the nozzle portion 14a.
  • the first outlet 16b and the nozzle portion 14a are directly connected.
  • the second outlet 16c is provided on the cylindrical surface portion of the distributor 16, that is, the outer peripheral wall.
  • the distributor 16 constitutes a centrifugal gas-liquid separator.
  • the shape of the housing 16e and the extending direction of the passage 16f toward the inflow port 16a are set so as to generate a swirling flow of the refrigerant in the distributor 16.
  • the passage 16 f extends in the tangential direction of the housing 16 e of the distributor 16.
  • the refrigerant flows from the inlet 16a into the separation chamber 16d after passing through the passage 16f. Thereby, the refrigerant swirls along the inner wall surface of the housing 16e. Further, the refrigerant flows toward the nozzle portion 14a while turning around the axis in the distributor 16. In this process, the liquid phase refrigerant is collected outside the separation chamber 16d by centrifugal force.
  • the gas phase refrigerant is collected in the center of the swirl chamber, that is, on the shaft.
  • Means for generating a swirling flow is provided by the shape of the inner wall surface of the housing 16e and the extending direction of the passage 16f.
  • the second outlet 16 c is connected to a passage communicating with the first space 29. At least a part of the passage is provided by a pipe 243 that serves as the decompressor 17 and the internal heat exchanger 40.
  • the pipe 243 is joined to the outer surface of the upper tank portion 15b that partitions the first space 26 so as to allow heat exchange.
  • the pipe 243 has an inner diameter and a length that cause a pressure loss necessary for the decompressor 17.
  • the pipe 243 is brazed to the outer surface of the upper tank portion 15b. As a result, the pipe 243 exchanges heat between the refrigerant in the first space 26 and the refrigerant in the pipe 243.
  • the refrigerant flowing into the distributor 16 from the refrigerant inlet 24 is branched into a first refrigerant flow toward the nozzle portion 14a and a second refrigerant flow toward the pipe 243.
  • the first refrigerant flow is reduced in pressure through the ejector 14, and is supplied to the first evaporator 15 as indicated by an arrow R1.
  • the refrigerant flows into the second space 27 of the upper tank portion 15b.
  • the refrigerant flows from the second space 27 toward the lower tank portion 15c through the plurality of tubes 21 in the right half of the core portion 15a as indicated by an arrow R2.
  • the refrigerant moves in the lower tank portion 15c as indicated by an arrow R3.
  • the refrigerant flows from the lower tank portion 15c toward the first space 26 of the upper tank portion 15b through the plurality of tubes 21 in the left half of the core portion 15a as indicated by an arrow R4. Thereafter, the refrigerant flows toward the refrigerant outlet 25 as indicated by an arrow R5.
  • the second refrigerant flow is depressurized by passing through the pipe 243.
  • the second refrigerant flow exchanges heat with the refrigerant in the first space 26 by passing through the pipe 243.
  • the second refrigerant stream is supercooled.
  • the decompressed low-pressure refrigerant is supplied to the second evaporator 18 as indicated by an arrow R6.
  • the refrigerant flows into the first space 29 of the upper tank portion 18b.
  • the refrigerant flows from the first space 29 toward the lower tank portion 18c through the plurality of tubes 21 in the left half of the core portion 18a as indicated by an arrow R7.
  • the refrigerant moves in the lower tank portion 18c as indicated by an arrow R8.
  • the refrigerant flows from the lower tank portion 18c toward the second space 30 of the upper tank portion 18b through the plurality of tubes 21 in the right half of the core portion 18a as indicated by an arrow R9. Thereafter, the refrigerant is sucked into the ejector 14 from the suction port 14b. Since the evaporator unit 220 has the flow path configuration as described above, it is only necessary to provide one refrigerant inlet 24 and one refrigerant outlet 25 as the evaporator unit 220 as a whole. (Third embodiment) In the said embodiment, the internal heat exchanger 40 was comprised by making the piping 243 contact the outer side of the upper side tank part 15b. Instead, in the third embodiment, as shown in FIG.
  • an outer wall member 343 is further provided outside the upper tank portion 15b.
  • the outer wall member 343 is provided so as to form a thin space between the upper tank portion 15b.
  • the decompressor 17 and the internal heat exchanger 40 are provided by the gap between the upper tank portion 15b and the outer wall member 343.
  • the refrigerant flowing out from the separation chamber 16d of the distributor 16 in the ejector case 23 via the second outlet 16c flows into the upper tank portion 18b after passing through the gap.
  • the internal heat exchanger 40 is disposed outside the upper tank portion 15b.
  • a pipe 443 for providing the upstream passage 41 is provided in the upper tank portion 15b.
  • the pipe 443 is provided so as to be able to exchange heat with the refrigerant in the upper tank portion 15b.
  • the decompressor 17 and the internal heat exchanger 40 are provided by the pipe 443.
  • the refrigerant that has flowed out from the separation chamber 16d of the distributor 16 in the ejector case 23 via the second outlet 16c passes through the pipe 443 and then flows into the upper tank portion 18b.
  • an additional part is employed to provide the internal heat exchanger 40.
  • an ejector case 523 that partitions the separation chamber 16 d of the distributor 16 is disposed inside the upper tank portion 15 b.
  • the ejector case 523 is provided so as to be able to exchange heat with the refrigerant in the upper tank portion 15b.
  • the liquid phase refrigerant separated in the separation chamber 16d exchanges heat with the refrigerant in the upper tank portion 15b via the ejector case 523, and then flows out from the second outlet 16c.
  • the piping 543 which provides the pressure reduction device 17 is provided.
  • the internal heat exchanger 40 is provided by the ejector case 523. (Sixth embodiment)
  • the distributor 16 and the internal heat exchanger 40 may be disposed between the decompressor 13 and the evaporator unit 620.
  • the evaporator unit 620 includes an ejector 14, a first evaporator 15, a decompressor 17, and a second evaporator 18.
  • a refrigerant distribution unit 650 is disposed between the decompressor 13 and the evaporator unit 620.
  • the decompressor 13, the refrigerant distribution unit 650, and the evaporator unit 620 are connected to each other by a detachable connecting means such as a bolt, and constitute a low-pressure component unit that can be handled as a single component.
  • the decompressor 13 and the refrigerant distribution unit 650 are configured as separate parts that can be separated from the evaporator unit 620.
  • the refrigerant distribution unit 650 forms the distributor 16 by forming the inlet 16a, the outlets 16b and 16c, and the separation chamber 16d. Further, the refrigerant distribution unit 650 forms the internal heat exchanger 40 by forming the upstream passage 41 and the downstream passage 42. Also in this embodiment, the refrigerant distribution unit 650 includes the distributor 16 and the internal heat exchanger 40. Further, the decompressor 17 may be disposed in the refrigerant distribution unit 650. (Seventh embodiment) In the said embodiment, the 1st evaporator 15 and the 2nd evaporator 18 were employ
  • the evaporator 15 is not provided on the downstream side of the ejector 14. According to this embodiment, the capability of the evaporator 18 arranged on the suction side of the ejector 14 can be improved.
  • the preferred embodiments of the present disclosure have been described above. However, the present disclosure is not limited to the above-described embodiments, and various modifications can be made without departing from the spirit of the present disclosure.
  • the structure of the said embodiment is an illustration to the last, Comprising: The range of this indication is not limited to the range of these description.
  • the scope of the present disclosure is indicated by the description of the scope of claims, and further includes meanings equivalent to the description of the scope of claims and all modifications within the scope.
  • the distributor 16 is provided by a centrifugal gas-liquid separator that uses a refrigerant flow.
  • a collision-type gas-liquid separator that separates the liquid-phase refrigerant and the gas-phase refrigerant by colliding the gas-liquid two-phase refrigerant with a member that easily captures the liquid refrigerant, or the gas-liquid two-phase refrigerant by gravity.
  • separation-type gas-liquid separators such as a reservoir-type gas-liquid separator that separates the liquid into a liquid-phase refrigerant and a gas-phase refrigerant can be employed.
  • distributor 16, the ejector 14, the 2nd decompressor 17, the 2nd evaporator 18, the 1st evaporator 15, and the internal heat exchanger 40 are included.
  • At least two of the plurality of low-pressure components are configured as an integral unit 220,650.
  • a combination of a plurality of low-pressure components different from the combination specifically illustrated in the above embodiment may be integrally configured. Further, all of the low-pressure components may be connected to each other by piping as separate components. According to this configuration, handling of a plurality of parts is facilitated.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Jet Pumps And Other Pumps (AREA)

Abstract

L'invention porte sur un cycle de réfrigération du type à éjecteur dans lequel un décompresseur (13) règle la quantité d'arrivée (G) d'un fluide frigorigène qui pénètre dans un distributeur (16). Le distributeur (16) distribue un fluide frigorigène à deux phases, gaz-liquide, décomprimé par le décompresseur (13). Plus précisément, un fluide frigorigène qui comprend plus d'une phase gazeuse que d'une phase liquide est fourni à un éjecteur (14), et un fluide frigorigène qui comprend plus d'une phase liquide que d'une phase gazeuse est fourni à un second évaporateur (18). Un échangeur de chaleur interne (40) échange de la chaleur entre le fluide frigorigène de pré-évaporation et le fluide frigorigène de post-évaporation dans le second évaporateur (18). Au moyen de l'échangeur de chaleur interne (40), le fluide frigorigène fourni au second évaporateur (18) est surrefroidi et la chaleur latente utilisable dans le second évaporateur (18) est augmentée. La performance d'absorption de chaleur du second évaporateur (18) est améliorée au moyen de l'échangeur de chaleur interne, de sorte que le débit volumétrique côté buse (Gn) distribué par l'éjecteur (14) peut être augmenté. Grâce à l'augmentation du débit volumétrique côté buse (Gn), l'éjecteur (14) peut présenter une performance suffisante.
PCT/JP2012/007317 2011-12-09 2012-11-15 Cycle de réfrigération du type à éjecteur WO2013084418A1 (fr)

Applications Claiming Priority (2)

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JP2011-270233 2011-12-09
JP2011270233 2011-12-09

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2015015726A1 (fr) * 2013-07-31 2015-02-05 株式会社デンソー Dispositif de conditionnement d'air pour véhicule

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2010266198A (ja) * 2005-04-01 2010-11-25 Denso Corp エジェクタ式冷凍サイクル
JP2011220552A (ja) * 2010-04-05 2011-11-04 Denso Corp 蒸発器ユニット

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2010266198A (ja) * 2005-04-01 2010-11-25 Denso Corp エジェクタ式冷凍サイクル
JP2011220552A (ja) * 2010-04-05 2011-11-04 Denso Corp 蒸発器ユニット

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2015015726A1 (fr) * 2013-07-31 2015-02-05 株式会社デンソー Dispositif de conditionnement d'air pour véhicule
JP2015030279A (ja) * 2013-07-31 2015-02-16 株式会社デンソー 車両用空調装置
US10371420B2 (en) 2013-07-31 2019-08-06 Denso Corporation Air conditioning device for vehicle

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