CN103477162A

CN103477162A - Heat exchange apparatus

Info

Publication number: CN103477162A
Application number: CN2012800182210A
Authority: CN
Inventors: 川上芳昭; 城岛悠树; 高桥荣三; 佐藤幸介; 内田和秀; 大野雄一
Original assignee: Toyota Motor Corp
Current assignee: Toyota Motor Corp
Priority date: 2011-04-13
Filing date: 2012-04-12
Publication date: 2013-12-25
Also published as: WO2012140492A3; JP2012218673A; EP2697576A2; US20140116082A1; JP5718710B2; WO2012140492A2

Abstract

A heat exchange apparatus (1) that performs heat exchange between a refrigerant and a temperature-adjusted unit (31) includes: a compressor (12) that circulates the refrigerant; a heat exchanger (14) that performs heat exchange between the refrigerant and outside air; an expansion valve (16) that reduces a pressure of the refrigerant; a heat exchanger (18) that performs heat exchange between the refrigerant and air-conditioning air; a cooling passage (32) that forms a path for the refrigerant to flow between the heat exchanger (14) and the expansion valve (16); and a heating passage (33) that forms a path for the refrigerant to flow between the expansion valve (16) and the heat exchanger (18). The temperature-adjusted unit (31) is disposed to be capable of exchanging heat with the refrigerant flowing through the cooling passage (32) and to be capable of exchanging heat with the refrigerant flowing through the heating passage (33).

Description

Heat-exchange device

Technical field

The present invention relates to a kind of heat-exchange device, and relate more particularly at the refrigerant of the steam compression type refrigerant cycles of flowing through and stand thermoregulator temperature be conditioned the heat-exchange device that carries out heat exchange between unit.

Background technology

The relevant correlation technique at the motor cooling device with for cooling CD-ROM drive motor, for example, Japanese Patent Application No.2005-218271(JP2005-218271A) a kind of technology has been proposed, wherein, when the temperature of CD-ROM drive motor and the temperature difference between oil temperature increase while exceeding predetermined value, oil that will be cooling by oil cooler is supplied to CD-ROM drive motor, and drops to predetermined value or when following, stop carrying out oil cooling but by oil cooler when the temperature of CD-ROM drive motor and the temperature difference between oil temperature.

In proposed another kind of technology, by the steam compression type refrigerant cycles that is used as Vehicular air-conditioning apparatus, carry out cooling heater.For example, Japanese Patent Application No.2007-69733(JP2007-69733A) a kind of system is disclosed, wherein the refrigerant pathway that extends to compressor from expansion valve, parallel deployment has with the idle call air and carries out the heat exchanger of heat exchange and the heat exchanger that carries out heat exchange with heater, and carrys out cooling heater by the refrigerant of using in aircondition.Japanese Patent Application No.2005-90862(JP2005-90862A) disclose a kind of cooling system, wherein in the bypass path of the pressure reducer of walking around the air-conditioning refrigerant cycles, evaporimeter and compressor, be provided with the heat-emitting element cooling apparatus for cooling heater.

Japanese Patent Application No.11-223406(JP11-223406A) a kind of configuration of used heat that absorbs from the heater such as power transistor for the refrigerant that makes heat pump cycle is disclosed.Japanese Patent Application No.9-290622(JP9-290622A) a kind of technology is disclosed, wherein from the used heat that is arranged on the heating part in vehicle, be collected and absorb the refrigerant sprayed for gas, effectively improve heating efficiency when externally air themperature is low thus, suppress the increase of power consumption simultaneously.

As a kind of cooling method that is arranged on the transaxle in vehicle, the heat of the dynamoelectric machine by such as forming transaxle or the generation of the heat generating components gear can be collected in automatic transmission fluids (ATF).Then ATF can be pumped into to the heat exchanger that is positioned at the transaxle outside in order to carry out heat exchange with cooling water or for the refrigerant of air conditioning.Must make ATF cooling, so that protection, such as the coil of dynamoelectric machine and the parts magnet, suppresses the deterioration of ATF, etc.Yet ATF not needs cooling all the time.As ATF, during by supercooling, the viscosity of ATF increases, and result, and gear may lack of lubrication and the increase of friction loss may be occurred.Therefore preferably make ATF heat to proper temperature.

Summary of the invention

The present invention considers the problems referred to above and designs, and a kind of heat-exchange device is provided, and utilizes described heat-exchange device, can suitably regulate the temperature that temperature is conditioned unit by with refrigerant, carrying out heat exchange.

According to an aspect of the present invention, a kind ofly be conditioned in refrigerant and temperature the heat-exchange device that carries out heat exchange between unit and comprise: compressor, the described refrigerant of described compressor compresses is in order to make described refrigerant circulate through described heat-exchange device; The first heat exchanger, described the first heat exchanger carries out heat exchange between described refrigerant and extraneous air; The first pressure reducer, described the first pressure reducer makes described refrigerant decompression; The second heat exchanger, described the second heat exchanger carries out heat exchange between described refrigerant and idle call air; The first path, described the first path forms for described refrigerant mobile path between described the first heat exchanger and described the first pressure reducer; And alternate path, described alternate path forms for described refrigerant mobile path between described the first pressure reducer and described the second heat exchanger.Described temperature is conditioned cell location and becomes can carry out heat exchange and can carry out heat exchange with the described refrigerant that flows through described alternate path with the described refrigerant that flows through described the first path.

Above-mentioned heat-exchange device also can comprise cross valve, and described cross valve switches the cryogen flow from described compressor to described the first heat exchanger and the cryogen flow from described compressor to described the second heat exchanger.

Above-mentioned heat-exchange device also can comprise: three-way, described three-way on the refrigerant paths between described the first heat exchanger and described the first pressure reducer with described the first path parallel join; With the first flow control valve, described first flow control valve is regulated the flow of the described refrigerant that flows through described the first path and is flow through the flow of the described refrigerant of described three-way.

Above-mentioned heat-exchange device also can comprise: the four-way road, described four-way road on the refrigerant paths between described the first pressure reducer and described the second heat exchanger with described alternate path parallel join; With the second control valve, described second control valve is regulated the flow of the described refrigerant that flows through described alternate path and is flow through the flow of the described refrigerant on described four-way road.

Above-mentioned heat-exchange device also can comprise the first open/close valve and the second open/close valve, and described the first path is opened and sealed to the described first open/close valve, and described alternate path is opened and sealed to the described second open/close valve.The described second open/close valve can cut out when the described first open/close valve is opened, and the described second open/close valve can be opened when the described first open/close valve cuts out.

Above-mentioned heat-exchange device also can comprise the second pressure reducer, described the second pressure reducer described the first heat exchanger and described temperature be conditioned between unit be arranged on described the first path in order to make described refrigerant decompression.

Above-mentioned heat-exchange device also can comprise: the five-way road, and described five-way road is in a part that forms described the first path and through described temperature, be conditioned on the path of unit and described the first heat exchanger and path parallel join through described the second pressure reducer; With the 3rd open/close valve, described the 3rd open/close valve is arranged in described five-way road in order to open and seal described five-way road.

Utilization is according to heat-exchange device of the present invention, can be by refrigerant and temperature, being conditioned and carrying out heat exchange between unit and suitably regulate the temperature that temperature is conditioned unit.

The accompanying drawing explanation

Below with reference to accompanying drawing in the detailed description of exemplary embodiment of the present invention, feature of the present invention, advantage and technology and industrial significance being described, similar Reference numeral means similar key element in the accompanying drawings, and wherein:

Fig. 1 is the schematic diagram illustrated according to the configuration of the heat-exchange device of the first embodiment of the present invention;

Fig. 2 is the mollier diagram (enthalpy-entropy diagram) be illustrated according to the refrigerant state between the cooling on-stream period of the steam compression type refrigerant cycles of the first embodiment;

Fig. 3 A, 3B, 3C and 3D are the schematic diagrames that the aperture control of the flow control valve shown in Fig. 1 is shown;

Fig. 4 is the schematic diagram that the heat-exchange device of the state be switched in the cross valve shown in Fig. 1 is shown.

Fig. 5 is the mollier diagram be illustrated according to the refrigerant state between the heating on-stream period of the steam compression type refrigerant cycles of the first embodiment;

Fig. 6 is the schematic diagram that the heat-exchange device when the temperature according to the first embodiment shown in Fig. 4 is conditioned unit and is heated is shown;

Fig. 7 is the mollier diagram that the state of the refrigerant used in the steam compression type refrigerant cycles according to the first embodiment when temperature is conditioned unit and is heated is shown;

Fig. 8 is the schematic diagram illustrated according to the configuration of the heat-exchange device of the second embodiment;

Fig. 9 is the mollier diagram be illustrated according to the refrigerant state between the cooling on-stream period of the steam compression type refrigerant cycles of the second embodiment;

Figure 10 is the schematic diagram that the heat-exchange device according to the second embodiment of the state be switched in the cross valve shown in Fig. 9 is shown.

Figure 11 is the mollier diagram be illustrated according to the refrigerant state between the heating on-stream period of the steam compression type refrigerant cycles of the second embodiment;

Figure 12 is the schematic diagram that the heat-exchange device when the temperature according to the second embodiment shown in Figure 10 is conditioned unit and is heated is shown;

Figure 13 is the mollier diagram that the state of the refrigerant used in the steam compression type refrigerant cycles according to the second embodiment when temperature is conditioned unit and is heated is shown;

Figure 14 is the schematic diagram illustrated according to the configuration of the heat-exchange device of the 3rd embodiment;

Figure 15 is the mollier diagram be illustrated according to the refrigerant state between the cooling on-stream period of the steam compression type refrigerant cycles of the 3rd embodiment;

Figure 16 is the schematic diagram that the heat-exchange device according to the 3rd embodiment of the state be switched in the cross valve shown in Figure 14 is shown; And

Figure 17 is the schematic diagram that the heat-exchange device when the temperature according to the 3rd embodiment shown in Figure 16 is conditioned unit and is heated is shown.

The specific embodiment

Hereinafter will embodiments of the invention be described based on accompanying drawing.Note, in the following drawings, identical or corresponding part is endowed identical Reference numeral, and does not repeat its explanation.

Fig. 1 is the schematic diagram illustrated according to the configuration of the heat-exchange device of the first embodiment.As shown in Figure 1, heat-exchange device 1 comprises steam compression type refrigerant cycles 10.This steam compression type refrigerant cycles 10 is arranged in vehicle so that cooling and heat for example vehicle interior of vehicle.When being for example ON or when the selected and temperature crew module is higher than design temperature for the automatic control mode that is automatically design temperature by the crew module's of vehicle adjustment for carrying out cooling switching over, utilize steam compression type refrigerant cycles 10 to carry out cooling.When being for example the selected and temperature crew module of ON or automatic control mode when lower than design temperature for the switching over of carrying out heating, utilize steam compression type refrigerant cycles 10 to be heated.

Steam compression type refrigerant cycles 10 comprises compressor 12, as the heat exchanger 14 of the first heat exchanger, as the expansion valve 16 of an example of pressure reducer with as the heat exchanger 18 of the second heat exchanger.Steam compression type refrigerant cycles 10 also comprises cross valve 13.Cross valve 13 is configured to can be in 14 cryogen flow of advancing and switching between 18 cryogen flow of advancing from compressor 12 towards heat exchanger from compressor 12 towards heat exchanger.

Motor or engine that compressor 12 utilization is arranged in vehicle operate as power source, with by refrigerant gas adiabatic be compressed into overheated refrigerant gas.Compressor 12 sucks and compresses gas phase refrigerant mobile when 10 operation of steam compression type refrigerant cycles, and emits the gas phase refrigerant of high temperature, high pressure.By emitting refrigerant, compressor 12 makes refrigerant cycle pass through steam compression type refrigerant cycles 10.

Heat exchanger

14,18 comprises respectively the pipe flow through for refrigerant and the fin that carries out heat exchange between the refrigerant that flows through pipe and

heat exchanger

14,18 ambient

airs.Heat exchanger

14,18 carries out heat exchange between refrigerant and the air stream of supplying with by the gravity-flow ventilation that occurs along with Vehicle Driving Cycle or the air stream supplied with by fan.

Expansion valve 16 expands by the liquid phase refrigerant that makes high pressure through small hole injection liquid phase refrigerant.As a result, the liquid phase refrigerant of high pressure becomes the vaporific refrigerant of low temperature, low pressure.Expansion valve 16 makes the refrigerant liquid decompression of condensation, to produce the damp steam in the gas-liquid mixed state.Note, the expansion valve 16 that is not limited to carry out throttling expansion for the pressure reducer that makes the refrigerant liquid decompression, and can be also capillary.

Steam compression type refrigerant cycles 10 also comprises refrigerant pathway 21 to 26.Refrigerant pathway 21 is connected to cross valve 13 by compressor 12.Refrigerant flows to cross valve 13 through refrigerant pathway 21 from compressor 12.Refrigerant pathway 22 is connected to heat exchanger 14 by cross valve 13.Through refrigerant pathway 22, the one from cross valve 13 and heat exchanger 14 flows to another one to refrigerant.Refrigerant pathway 23 is connected to expansion valve 16 by heat exchanger 14.Through refrigerant pathway 23, the one from heat exchanger 14 and expansion valve 16 flows to another one to refrigerant.

Refrigerant pathway 24 is connected to heat exchanger 18 by expansion valve 16.Through refrigerant pathway 24, the one from expansion valve 16 and heat exchanger 18 flows to another one to refrigerant.Refrigerant pathway 25 is connected to cross valve 13 by heat exchanger 18.Through refrigerant pathway 25, the one from heat exchanger 18 and cross valve 13 flows to another one to refrigerant.Refrigerant pathway 26 is connected to compressor 13 by cross valve 13.Refrigerant flows to compressor 12 through refrigerant pathway 26 from cross valve 13.

Steam compression type refrigerant cycles 10 is by utilizing refrigerant pathway 21 to 26 that compressor 12, heat exchanger 14, expansion valve 16 and heat exchanger 18 are connected to each other and form.Note, can use the refrigerant as steam compression type refrigerant cycles 10 such as carbon dioxide, hydrocarbon such as propane or iso-butane, ammonia, water etc.

The first path and as the refrigerant pathway 23a parallel join of three-way and be arranged on for refrigerant along it on path mobile between heat exchanger 14 and expansion valve 16.Refrigerant pathway 23a forms the part as the refrigerant pathway 23 of the refrigerant paths between heat exchanger 14 and expansion valve 16.Be provided with heat exchange unit 30 on the first path.Heat exchange unit 30 is arranged on the refrigerant paths between heat exchanger 14 and expansion valve 16.Heat exchange unit 30 comprises that standing thermoregulator temperature is conditioned unit 31, and the cooling channel 32 consisted of the pipe flow through for refrigerant.Heat-exchange device 1 comprises as not passing the refrigerant pathway 23a in the path of heat exchange unit 30, and comprises

refrigerant pathway

52,54,55 and the cooling channel 32 as the path through heat exchange unit 30.Refrigerant paths between heat exchanger 14 and expansion valve 16 is branched off into a part that makes refrigerant and flows to heat exchange unit 30.

Refrigerant pathway

52,54,55 is set to flow to the path of cooling channel 32 for refrigerant along it.An end of cooling channel 32 is connected to refrigerant pathway 54, and another end of cooling channel 32 is connected to refrigerant pathway 55.Refrigerant pathway 52 and refrigerant pathway 54 are communicated with via open/close valve 53.Refrigerant flows in cooling channel 32 through

refrigerant pathway

52,54 or refrigerant pathway 55 from refrigerant pathway 23.Flow through the refrigerant of cooling channel 32 and temperature and be conditioned unit 31 and carry out heat exchange, and then the another one in

refrigerant pathway

52,54 and refrigerant pathway 55 is returned to refrigerant pathway 23.With the first path of refrigerant pathway 23a parallel join comprise heat exchanger 14 sides of heat exchange unit 30

refrigerant pathway

52,54, be arranged on the refrigerant pathway 55 of expansion valve 16 sides of cooling channel 32 in heat exchange unit 30 and heat exchange unit 30.The first path is opened and sealed to open/close valve 53.

Mobile cryogen flow supercooling path 32 between heat exchanger 14 and expansion valve 16.When flowing through cooling channel 32, refrigerant comes chilling temperature to be conditioned unit 31 by be conditioned unit 31 heat absorptions from temperature.Heat exchange unit 30 is configured to be conditioned between the refrigerant in unit 31 and cooling channel 32 and to carry out heat exchange in temperature.In this embodiment, for example, heat exchange unit 30 comprises cooling channel 32, and this cooling channel forms the housing that makes its outer peripheral face and temperature be conditioned unit 31 and directly contacts.Cooling channel 32 comprises the part that is conditioned the housing adjacency of unit 31 with temperature.In this part, can be conditioned between unit 31 and carry out heat exchange in the refrigerant that flows through cooling channel 32 and temperature.

Temperature is conditioned unit 31 and is cooled by being directly connected to the outer peripheral face of cooling channel 32 of a part that extends to the refrigerant paths of expansion valve 16 from heat exchanger 14 that forms steam compression type refrigerant cycles 10.Because temperature is conditioned on the outside that unit 31 is configured in cooling channel 32, therefore being conditioned unit 31, temperature can not disturb the cryogen flow of the inside of flowing through cooling channel 32.Therefore, the pressure loss in steam compression type refrigerant cycles 10 can not increase, and therefore can be conditioned unit 31 in the situation that do not increase the power chilling temperature of compressor 12.

Alternatively, heat exchange unit 30 can comprise that Jie is located at the heat pipe that temperature is conditioned any conventional between unit 31 and cooling channel 32.In this case, temperature is conditioned unit 31 and is connected to the outer peripheral face of cooling channel 32 and is cooled by via this heat pipe, from temperature, being conditioned the heat that unit 31 is delivered to cooling channel 32 via this heat pipe.Be set as the heat pipe heating part and cooling channel 32 is set as to the heat pipe cooling end by temperature being conditioned to unit 31, can improve cooling channel 32 and temperature and be conditioned the heat transference efficiency between unit 31, thereby the efficiency that makes chilling temperature be conditioned unit 31 improves.Can use for example tube core formula (Wick) heat pipe.

Can utilize this heat pipe to be conditioned unit 31 from temperature conducts heat reliably to cooling channel 32, and so temperature is conditioned unit 31 and cooling channel 32 can away from each other, needn't arrange with complicated layout cooling channel 32 to guarantee that cooling channel 32 and temperature are conditioned unit 31 and contact thus.As a result, can improve the configuration free degree that temperature is conditioned unit 31.

As the

refrigerant pathway

52,54,55 through the path of heat exchange unit 30 and cooling channel 32 with as not through the parallel path that supplies refrigerant mobile between heat exchanger 14 and expansion valve 16 along it that is set to of refrigerant pathway 23a in the path of crosspoint 30.What comprise

refrigerant pathway

52,54,55 is conditioned cooling system and the refrigerant pathway 23a parallel join of unit 31 for temperature.Do not pass the path of the refrigerant of heat exchange unit 30 by flowing and be arranged to parallel with the path of the refrigerant that passes heat exchange unit 30 and only make a refrigerant part flow to

refrigerant pathway

52,54,55 between heat exchanger 14 and expansion valve 16, only make the part of refrigerant mobile between heat exchanger 14 and expansion valve 16 flow to heat exchange unit 30.

In heat exchange unit 30, can not make chilling temperature be conditioned the required a certain amount of cryogen flow in unit 31 makes all refrigerant all flow to the situation of heat exchange unit 30 to

refrigerant pathway

52,54,55.Therefore, suitably chilling temperature is conditioned unit 31, and can prevent that temperature is conditioned the supercooling of unit 31.In addition, can reduce and flow to the pressure loss of refrigerant that is conditioned the cooling system (comprising

refrigerant pathway

52,54,55 and cooling channel 32) of unit 31 for temperature, thereby can realize making compressor 12 runnings in order to make the corresponding reduction of the required electric power amount of refrigerant cycle.

For example, temperature be conditioned unit 31 be by with carry out heat exchange and the ATF cooler of cooling ATF with acting on the lubricating oil that is arranged on the transaxle in vehicle and the ATF of hydraulic oil.ATF is charged the inside of not shown transaxle, so that the corresponding building block of Cooling and Lubricator transaxle.For this purpose, ATF flows to temperature from transaxle through not shown pipe and is conditioned unit 31, and the refrigerant be conditioned in unit 31 with temperature carries out heat exchange, and then through not shown pipe, returns to transaxle.

Heat exchanger 18 is configured in the inside of the pipeline 40 flow through for air.Heat exchanger 18 is by refrigerant and flow through between the idle call air of pipeline 40 and carry out the temperature that the idle call air is regulated in heat exchange.Pipeline 40 comprises entrance 41 and pipe outlet 42, and this entrance is the entrance of idle call air in its flow ipe 40, and this pipe outlet is the outlet that the idle call air flows out from pipeline 40 through it.Near internal configurations at pipeline 40 entrance 41 has fan 43.

When fan 43 is driven, air stream piping 40.When fan 43 running, the idle call air is through the inside of entrance 41 flow ipes 40.Air in flow ipe 40 can be the air in the crew module of extraneous air or vehicle.Arrow in Fig. 1 45 means to flow through heat exchanger 18 so that the idle call air stream that carries out heat exchange with the refrigerant of steam compression type refrigerant cycles 10.In heat exchanger 18 between cooling on-stream period, the idle call air is accepted heat transmission from the idle call air in order to be cooled under heated state at refrigerant.In heat exchanger 18 between the heating on-stream period, the idle call air conducts heat in order to be heated under the state be cooled to the idle call air at refrigerant.Arrow 46 means to be in heat exchanger 18 after standing adjustment the idle call air stream flowed out from pipeline 40 through pipe outlet 42.

Between cooling on-stream period, refrigerant flows through steam compression type refrigerant cycles 10 so that in turn through A point, B point, C point, D point and E point, as shown in Figure 1.Thereby refrigerant circulates between compressor 12, heat exchanger 14, expansion valve 16 and heat exchanger 18.Refrigerant is through by utilizing refrigerant pathway 21 to 26 to connect in turn refrigerant cycle path that compressor 12, heat exchanger 14, expansion valve 16 and heat exchanger 18 form in the interior circulation of steam compression type refrigerant cycles 10.

Fig. 2 is the mollier diagram be illustrated according to the refrigerant state between the cooling on-stream period of the steam compression type refrigerant cycles 10 of the first embodiment.Transverse axis in Fig. 2 means that (unit: kJ/kg), and the longitudinal axis means the absolute pressure (unit: MPa) of refrigerant for the specific enthalpy of refrigerant.The saturated vapor line that curve in figure is refrigerant and saturated liquidus.Fig. 2 illustrate refrigerant refrigerant from compressor 12 via heat exchanger 14 flow in refrigerant pathways 23, chilling temperature is conditioned unit 31, return to refrigerant pathway 23 and then via expansion valve 16 and heat exchanger 18, return to the thermodynamic state of each point (that is, A, B, C, D and E point) of the steam compression type refrigerant cycles 10 of compressor 12.

As shown in Figure 2, be inhaled into refrigerant (A point) in compressor 12 along how much entropy lines insulated compression in compressor 12 under the superheated vapor state.Along with refrigerant is compressed, its pressure and temperature rises, and makes refrigerant become high temperature, high pressure, high overheated steam (B point).Then refrigerant flow to heat exchanger 14.

High-pressure refrigerant steam in inflow heat exchanger 14 carries out heat exchange and is cooled thus with extraneous air in heat exchanger 14.As a result, refrigerant becomes dry saturation vapor from superheated vapor remaining under the state of constant pressure.Condensation latent heat is released, and makes refrigerant liquefy gradually, becomes thus the damp steam in the gas-liquid mixed state, and, when the refrigerant total condensation, forms saturated solution.In addition, sensible heat is released, and makes and forms supercooling liquid (C point).Heat exchanger 14 by will be in compressor 12 heat of compressed superheated refrigerant gas isobaric be released to external agency and form refrigerant liquid.The gas phase refrigerant of emitting from compressor 12 by heat releases around heat exchanger 14 so that refrigerant is cooled and condensation (liquefaction).As carry out the result of heat exchange in heat exchanger 14, the temperature of refrigerant descends, and makes refrigerant liquefaction.

High pressure liquid phase refrigerant by heat exchanger 14 liquefaction flows to heat exchange unit 30 through refrigerant pathway 52, open/close valve 53 and refrigerant pathway 54 successively, and chilling temperature is conditioned unit 31.As with temperature, being conditioned the result that unit 31 carries out heat exchange, the supercooling degree of refrigerant reduces.More specifically, the refrigerant in the supercooling liquid status heats up and approaches the liquid cryogen saturation temperature receiving while from temperature, being conditioned the sensible heat of unit 31, by this refrigerant is heated to the temperature (D point) a little less than saturation temperature.Next, refrigerant flows in expansion valve 16 through refrigerant pathway 23.By passing expansion valve 16, the refrigerant in the supercooling liquid status, by throttling expansion, makes the temperature and pressure of refrigerant descend when its specific enthalpy remains unchanged.As a result, refrigerant becomes in the low temperature of gas-liquid mixed state, the damp steam of low pressure (some E).

The refrigerant of the damp steam state of emitting from expansion valve 16 is in refrigerant pathway 24 inflow heat exchangers 18.The refrigerant of damp steam state flows in the pipe of heat exchanger 18.When flowing through the pipe of heat exchanger 18, the hotwork that refrigerant absorbs from the idle call air via fin is evaporation latent heat, and result, and refrigerant evaporates when remaining in constant pressure.When refrigerant becomes dry saturation vapor fully, the temperature of refrigerant vapor further rises by sensible heat, and result, has formed superheated vapor (A point).In heat exchanger 18, refrigerant absorbs heat on every side and is heated.Then the refrigerant of evaporation flow in cross valve 13 through refrigerant pathway 25, and then via refrigerant pathway 26, be inhaled in compressor 12.The refrigerant that compressor 12 compressions come from heat exchanger 18 streams.According to this circulation, refrigerant experiences several times state variation, also i.e. compression, condensation, throttling expansion and evaporation repeatedly and continuously.

Note, above in the description to the steam compression type refrigerant cycles, describing theoretical refrigerant cycles.Yet, much less, in actual steam compression type refrigerant cycles 10, the loss in necessary considering compression machine 12 and the pressure loss and the heat loss of refrigerant.

Between cooling on-stream period, heat exchanger 18 absorbs heat from importing into the surrounding air contacted with heat exchanger 18 along with the vaporific refrigerant gasification of the inside of flowing through heat exchanger 18.Heat exchanger 18 uses by low temperature, the low-pressure refrigerant of expansion valve 16 throttling expansions and decompression, and the heat of evaporation produced when the damp steam of refrigerant flashes to refrigerant gas with the idle call absorption of air in the crew module by from flowing into vehicle is carried out the crew module of cooling vehicle.The idle call air that temperature reduces when the heat of idle call air is absorbed by heat exchanger 18 flows in the crew module of vehicle, and result, the cooling crew module of vehicle.

Under the state of steam compression type refrigerant cycles 10 runnings, refrigerant carrys out cooling crew module by the absorption of air heat of evaporation from the crew module of vehicle in heat exchanger 18.The high-pressure liquid refrigerant of emitting from heat exchanger 14 in addition, flows in heat exchange unit 30 and chilling temperature is conditioned unit 31 by with temperature, being conditioned that unit 31 carries out heat exchange.Therefore, the cooling temperature that is arranged on vehicle of steam compression type refrigerant cycles 10 that heat-exchange device 1 utilization is carried out air conditioning for the crew module to vehicle is conditioned unit 31.Note, temperature be conditioned unit 31 to be cooled to temperature preferably at least low than the higher limit of the target temperature range of the temperature range that is conditioned unit 31 as temperature.

Get back to Fig. 1, heat-exchange device 1 comprises flow control valve 51.Flow control valve 51 is configured in the refrigerant pathway 23a of a part that forms the refrigerant pathway 23 between heat exchanger 14 and expansion valve 16.Increase or reduce to flow through the pressure loss of the refrigerant of refrigerant pathway 23a by the valve opening that changes flow control valve 51, and result, flow control valve 51 is regulated the flow of the refrigerant that flows through refrigerant pathway 23a by expectation and is flow through the flow of the refrigerant of

refrigerant pathway

52,54,55 and cooling channel 32.

For example, close fully and while making its valve opening be set to 0%, all refrigerant that flow between heat exchanger 14 and expansion valve 16 flow in

refrigerant pathways

52,54,55 and cooling channel 32 when flow control valve 51.When the valve opening of flow control valve 51 increases, the flow that flows through the refrigerant of refrigerant pathway 23a between heat exchanger 14 and expansion valve 16 in mobile refrigerant increases, and flows through

refrigerant pathway

52,54,55 and cooling channel 32 reduces so that chilling temperature is conditioned the flow of the refrigerant of unit 31.When the valve opening of flow control valve 51 reduces, the flow that flows through the refrigerant of refrigerant pathway 23a between heat exchanger 14 and expansion valve 16 in mobile refrigerant reduces, and flows through

refrigerant pathway

52,54,55 and cooling channel 32 increases so that chilling temperature is conditioned the flow of the refrigerant of unit 31.

When the valve opening of flow control valve 51 increases, the flow that chilling temperature is conditioned the refrigerant of unit 31 reduces, thereby the ability that makes chilling temperature be conditioned unit 31 reduces.When the valve opening of flow control valve 51 reduces, the flow that chilling temperature is conditioned the refrigerant of unit 31 increases, thereby the ability that makes chilling temperature be conditioned unit 31 improves.The amount that can use traffic control valve 51 will flow to the refrigerant of heat exchange unit 30 is adjusted to optimised quantity, and therefore can prevent reliably that temperature is conditioned the supercooling of unit 31.In addition, can reduce reliably through the pressure loss of the cryogen flow of

refrigerant pathway

52,54,55 and cooling channel 32 and make the power consumption of the required compressor of refrigerant cycle 12.

Now an example of the control of carrying out for the valve opening of adjust flux control valve 51 will be described.Fig. 3 A to 3D is the schematic diagram that the aperture control of flow control valve 51 is shown.The transverse axis of the curve map shown in Fig. 3 A to 3D means the time.It is valve openings of using in the situation of electric expansion valve of stepper motor that the longitudinal axis of the curve map in Fig. 3 A is illustrated in flow control valve 51.It is the valve openings that are manipulated in the situation of the temperature-type expansion valve opened and closed in response to variations in temperature that the longitudinal axis of the curve map in Fig. 3 B is illustrated in flow control valve 51.The longitudinal axis of the curve map in Fig. 3 C means that temperature is conditioned the temperature of unit 31.The longitudinal axis of the curve map in Fig. 3 D means that temperature is conditioned the outlet of unit 31 and the temperature difference between entrance.

Temperature is conditioned unit 31 along with refrigerant is cooled through heat exchange unit 30.For example, be conditioned by monitor temperature the aperture that the temperature of unit 31 or outlet temperature that temperature is conditioned unit 31 and the temperature difference between inlet temperature are carried out adjust flux control valve 51.With reference to the curve map in Fig. 3 C, for example, by arranging, measure continuously the temperature sensor that temperature is conditioned the temperature of unit 31 and come monitor temperature to be conditioned the temperature of unit 31.In addition, with reference to the curve map in Fig. 3 D, for example, by arranging, the measurement temperature is conditioned the inlet temperature of unit 31 and the temperature sensor of outlet temperature comes monitor temperature to be conditioned the outlet of unit 31 and the temperature difference between entrance.

For example, when the temperature that is conditioned unit 31 when temperature surpasses the outlet that target temperature or temperature be conditioned unit 31/entrance temperature difference and surpasses the target temperature difference (, 3 to 5 ℃), the aperture of flow control valve 51 reduces, as shown in the curve map in Fig. 3 A and 3B.As mentioned above, when the aperture of flow control valve 51 narrows down, the flow that flows to the refrigerant of heat exchange unit 30 increases, and therefore more effectively chilling temperature be conditioned unit 31.Result, the temperature that can make temperature be conditioned unit 31 is reduced to target temperature or lower than target temperature, as shown in the curve map in Fig. 3 C, or can make temperature be conditioned the outlet of unit 31/entrance temperature difference to be reduced to the target temperature difference or following, as shown in the curve map in Fig. 3 D.

By the valve opening of adjust flux control valve 51 best in this way, can guarantee, for obtaining, temperature is conditioned to the amount of refrigerant that unit 31 remains on heat-sinking capability required in suitable temperature range, and result, suitably chilling temperature is conditioned unit 31.Therefore, can suppress reliably because the overheated temperature that makes is conditioned the situation that unit 31 damages.

Fig. 4 is the schematic diagram that the heat-exchange device 1 of the state be switched in cross valve 13 is shown.Comparison diagram 1 and 4, cross valve 13 is half-twist, thus switching for from the outlet of compressor 12, flow into refrigerant in cross valve 13 along it from cross valve 13 paths that emit.Between the cooling on-stream period shown in Fig. 1, the refrigerant compressed by compressor 12 flows to heat exchanger 14 from compressor 12.On the other hand, between the heating on-stream period shown in Fig. 4, the refrigerant compressed by compressor 12 flows to heat exchanger 18 from compressor 12.

Between the heating on-stream period, refrigerant flows through steam compression type refrigerant cycles 10 so that in turn through A point, B point, E point, D point and C point, as shown in Figure 4.Thereby refrigerant circulates between compressor 12, heat exchanger 18, expansion valve 16 and heat exchanger 14.Refrigerant is through by utilizing refrigerant pathway 21 to 26 to connect in turn refrigerant cycle path that compressor 12, heat exchanger 18, expansion valve 16 and heat exchanger 14 form in the interior circulation of steam compression type refrigerant cycles 10.

Fig. 5 is the mollier diagram be illustrated according to the refrigerant state between the heating on-stream period of the steam compression type refrigerant cycles 10 of the first embodiment.Transverse axis in Fig. 5 means that (unit: kJ/kg), and the longitudinal axis means the absolute pressure (unit: MPa) of refrigerant for the specific enthalpy of refrigerant.The saturated vapor line that curve in figure is refrigerant and saturated liquidus.Fig. 5 illustrate refrigerant refrigerant via heat exchanger 18 and expansion valve 16 from compressor 12 flow in refrigerant pathways 23, chilling temperature is conditioned unit 31, return to refrigerant pathway 23 and then via heat exchanger 14, return to the thermodynamic state of each point (that is, A, B, E, D and C point) of the steam compression type refrigerant cycles 10 of compressor 12.

As shown in Figure 5, be inhaled into refrigerant (A point) in compressor 12 along how much entropy lines insulated compression in compressor 12 under the superheated vapor state.Along with refrigerant is compressed, its pressure and temperature rises, and makes refrigerant become high temperature, high pressure, high overheated steam (B point).Then refrigerant flow to heat exchanger 18.

High-pressure refrigerant steam in inflow heat exchanger 18 is cooled in order to become dry saturation vapor from superheated vapor when remaining in constant pressure in heat exchanger 18.Condensation latent heat is released, and makes refrigerant liquefy gradually, becomes thus the damp steam in the gas-liquid mixed state, and, when the refrigerant total condensation, forms saturated solution.In addition, sensible heat is released, and makes and forms supercooling liquid (E point).Heat exchanger 18 by will be in compressor 12 heat of compressed superheated refrigerant gas isobaric be released to external agency and form refrigerant liquid.The gas phase refrigerant of emitting from compressor 12 by heat releases around heat exchanger 18 so that refrigerant is cooled and condensation (liquefaction).As carry out the result of heat exchange in heat exchanger 18, the temperature of refrigerant descends, and makes refrigerant liquefaction.Thereby refrigerant is cooled by heat release around heat exchanger 18.

High pressure liquid phase refrigerant by heat exchanger 18 liquefaction flows in expansion valve 16 through refrigerant pathway 24.In expansion valve 16, the refrigerant of supercooled liquid state, by throttling expansion, makes the temperature and pressure of refrigerant descend when the specific enthalpy of refrigerant remains unchanged, and result, has formed in the low temperature of gas-liquid mixed state, the damp steam of low pressure (D point).The refrigerant that reduces temperature by expansion valve 16 in

refrigerant pathway

23,55 flows into the cooling channel 32 of heat exchange units 30 also chilling temperature be conditioned unit 31.As with temperature, being conditioned the result that unit 31 carries out heat exchange, refrigerant is heated, and makes the aridity of refrigerant increase.When refrigerant is conditioned unit 31 and receives latent heat from temperature, the one partial gasification, thus make the ratio of the saturated vapor in the refrigerant of damp steam state increase (C point).

The refrigerant of the damp steam state of emitting from heat exchange unit 30 returns to refrigerant pathway 23 through

refrigerant pathway

54,52, and then in inflow heat exchanger 14.The refrigerant of damp steam state flows in the pipe of heat exchanger 14.When flowing through this pipe, refrigerant via fin from extraneous air heat absorption as evaporation latent heat, and result, refrigerant evaporates remaining under the state of constant pressure.When refrigerant becomes dry saturation vapor fully, the temperature of refrigerant vapor further rises by sensible heat, and result, and refrigerant vapor becomes superheated vapor (A point).The refrigerant of gasification is inhaled in compressor 12 via refrigerant pathway 22.The refrigerant that compressor 12 compressions come from heat exchanger 14 streams.According to this circulation, refrigerant experiences several times state variation, also i.e. compression, condensation, throttling expansion and evaporation repeatedly and continuously.

Between the heating on-stream period, heat exchanger 18 increases heat along with the refrigerant vapor condensation of the inside of flowing through heat exchanger 18 to importing into the surrounding air contacted with heat exchanger 18.Heat exchanger 18 use by compressor 12 adiabatic the high temperature, the refrigerant of high pressure that compress, emit with the idle call air in the crew module by flowing into vehicle the crew module that the condensation heat produced heats vehicle when refrigerant gas is condensed into the refrigerant damp steam.The idle call air that temperature rises after being heated from heat exchanger 18 flows in the crew module of vehicle, and result, and the crew module of vehicle is heated.

In heat-exchange device 1, alternate path and as the refrigerant pathway 24a parallel join on four-way road and be arranged on for refrigerant along it on path mobile between expansion valve 16 and heat exchanger 18.Refrigerant pathway 24a forms the part of refrigerant pathway 24, the refrigerant paths that refrigerant pathway 24 forms between expansion valve 16 and heat exchanger 18.Heat exchange unit 30 is arranged to carry out heat exchange with the first path as mentioned above, and is arranged in alternate path in order to can carry out heat exchange with alternate path.Heat exchange unit 30 is arranged on the refrigerant paths between expansion valve 16 and heat exchanger 18.Except temperature is conditioned unit 31 and cooling channel 32, heat exchange unit 30 also comprise by the pipe flow through for refrigerant, formed add heat passage 33.Heat-exchange device 1 comprises as not passing the refrigerant pathway 24a in the path of heat exchange unit 30, and comprises conduct through the

refrigerant pathway

62,64,65 in the path of heat exchange unit 30 and add heat passage 33.Refrigerant paths between expansion valve 16 and heat exchanger 18 is branched off into a part that makes refrigerant and flows to heat exchange unit 30.

Refrigerant pathway

62,64,65 is set to flow to along it path that adds heat passage 33 for refrigerant.An end that adds heat passage 33 is connected to refrigerant pathway 64, and another end that adds heat passage 33 is connected to refrigerant pathway 65.Refrigerant pathway 62 and refrigerant pathway 64 are communicated with via open/close valve 63.Refrigerant adds in heat passage 33 through

refrigerant pathway

62,64 or refrigerant pathway 65 inflows from refrigerant pathway 24.Flow through the refrigerant that adds heat passage 33 and temperature and be conditioned unit 31 and carry out heat exchange, and then the another one in

refrigerant pathway

62,64 and refrigerant pathway 65 is returned to refrigerant pathway 24.With the alternate path of refrigerant pathway 24a parallel join comprise heat exchanger 18 sides that are arranged in heat exchange unit 30

refrigerant pathway

62,64, be arranged on adding heat passage 33 and being positioned at the refrigerant pathway 65 of expansion valve 16 sides of heat exchange unit 30 of heat exchange unit 30.Open/close valve 63 is opened and the sealing alternate path.

Fig. 6 is the schematic diagram that the heat-exchange device 1 when temperature is conditioned unit 31 and is heated is shown.When wanting the temperature shown in cooling Fig. 1 and 4 to be conditioned unit 31, open/close valve 53 is opened, and open/close valve 63 cuts out.When open/close valve 53 is opened, open/close valve 63 cuts out.Therefore, cryogen flow supercooling path 32 but do not flow through and add heat passage 33.Heat is conditioned unit 31 from temperature and is delivered to the refrigerant that flows through cooling channel 32, and result, and temperature is conditioned unit 31 and is cooled.On the other hand, in the time will heating the temperature shown in Fig. 6 and be conditioned unit 31, open/close valve 63 is opened, and open/close valve 53 cuts out.When open/close valve 53 cuts out, open/close valve 63 is opened.Therefore, refrigerant flows through heating path 33 but does not flow through cooling channel 32.Heat is delivered to temperature and is conditioned unit 31 from flowing through the refrigerant that adds heat passage 33, and result, and temperature is conditioned unit 31 and is heated.

As shown in Figure 6, when via adding heat passage 33 mobile refrigerant between expansion valve 16 and heat exchanger 18, flowing through heating during path 33, temperature is conditioned unit 31 and is heated, and the temperature that raises thus is conditioned the temperature of unit 31.Heat exchange unit 30 is configured to carry out heat exchange between the refrigerant in temperature is conditioned unit 31 and adds heat passage 33.Be similar to the configuration that temperature is conditioned unit 31 in cooling channel 32, add the housing that the outer peripheral face of heat passage 33 can be directly be conditioned unit 31 with temperature and contact.Alternatively, be conditioned unit 31 and add between heat passage 33 in temperature and may be configured with heat pipe, make to add heat passage 33 and be set to heat pipe heating part and temperature and be conditioned unit 31 and be set to the heat pipe cooling end.Therefore be configured in because temperature is conditioned unit 31 outside that adds heat passage 33, therefore the pressure loss in steam compression type refrigerant cycles 10 can not increase, and can be conditioned unit 31 in the situation that do not increase the power heating-up temperature of compressor 12.

As the

refrigerant pathway

62,64,65 through the path of heat exchange unit 30 and add heat passage 33 with as not through the parallel path that supplies refrigerant mobile between expansion valve 16 and heat exchanger 18 along it that is set to of refrigerant pathway 24a in the path of heat exchange unit 30.What comprise

refrigerant pathway

62,64,65 is conditioned heating system and the refrigerant pathway 24a parallel join of unit 31 for temperature.Do not pass the path of the refrigerant of heat exchange unit 30 by flowing and be arranged to parallel with the path of the refrigerant that passes heat exchange unit 30 and only make the part of refrigerant flow to

refrigerant pathway

62,64,65 between expansion valve 16 and heat exchanger 18, only make the part of refrigerant mobile between expansion valve 16 and heat exchanger 18 flow to heat exchange unit 30.

In heat exchange unit 30, can not make heating-up temperature be conditioned the required a certain amount of cryogen flow in unit 31 makes all refrigerant all flow to the situation of heat exchange unit 30 to

refrigerant pathway

62,64,65.Therefore, suitably heating-up temperature is conditioned unit 31, and it is overheated to prevent that temperature is conditioned unit 31.In addition, can reduce and flow to the pressure loss of refrigerant that is conditioned the heating system (comprise

refrigerant pathway

62,64,65 and add heat passage 33) of unit 31 for temperature, thereby realize making compressor 12 runnings in order to make the corresponding reduction of the required electric power amount of refrigerant cycle.

Dispose flow control valve 61 as another flow control valve different from flow control valve 51 in refrigerant pathway 24a.Be similar to above-mentioned flow control valve 51, increase or reduce to flow through the pressure loss of the refrigerant of refrigerant pathway 24a by the valve opening that changes flow control valve 61, and result, flow control valve 61 is regulated the flow of the refrigerant flow through refrigerant pathway 24a by expectation and is flow through

refrigerant pathway

62,64,65 and add the flow of the refrigerant of heat passage 33.

When the valve opening of flow control valve 61 increases, the flow that is conditioned the refrigerant of unit 31 for heating-up temperature reduces, thereby the temperature that makes to raise is conditioned the ability of the temperature of unit 31, reduces.When the valve opening of flow control valve 61 reduces, the flow that is conditioned the refrigerant of unit 31 for heating-up temperature increases, thereby the temperature that makes to raise is conditioned the ability of the temperature of unit 31, improves.Utilize flow control valve 61, the amount that flows to the refrigerant of heat exchange unit 30 can be adjusted to optimised quantity, and therefore can prevent reliably that temperature is conditioned the overheated of unit 31.In addition, can reduce reliably through

refrigerant pathway

62,64,65 and add heat passage 33 cryogen flow the pressure loss and reduce the electric power amount that compressor 12 consumes in order to make refrigerant cycle.

Note, when temperature is conditioned unit 31 and is cooled, flow control valve 61 remains in full-gear, controls like that described with reference to Figure 3 the aperture of flow control valve 51 simultaneously.By closing open/close valve 63, can prevent reliably that refrigerant from flowing in heating path 33, and, by making flow control valve 61 standard-sized sheets, can reduce to greatest extent the pressure loss of the refrigerant that flows through refrigerant pathway 24a.On the other hand, when temperature is conditioned unit 31 and is heated, flow control valve 51 remains in full-gear, be similar to reference to the described aperture to flow control valve 51 of Fig. 3 simultaneously and control and the aperture of control flow control valve 61, that is, make it possible to add heat passage 33 by flowing through and remain on proper level so that heating-up temperature is conditioned the flow of the refrigerant of unit 31.By closing open/close valve 53, can prevent reliably that refrigerant from flowing in cooling channel 32, and, by making flow control valve 51 standard-sized sheets, can reduce to greatest extent the pressure loss of the refrigerant that flows through refrigerant pathway 23a.

Fig. 7 is the mollier diagram that the state of the refrigerant used in the steam compression type refrigerant cycles 10 according to the first embodiment when temperature is conditioned unit 31 and is heated is shown.Transverse axis in Fig. 7 means that (unit: kJ/kg), and the longitudinal axis means the absolute pressure (unit: MPa) of refrigerant for the specific enthalpy of refrigerant.The saturated vapor line that curve in figure is refrigerant and saturated liquidus.Fig. 7 illustrate refrigerant refrigerant via heat exchanger 18 from compressor 12 flow in refrigerant pathways 24, heating-up temperature is conditioned unit 3, return to refrigerant pathway 24 and then via expansion valve 16 and heat exchanger 14, return to the thermodynamic state of each point (that is, A, B, E, F and D point) of the steam compression type refrigerant cycles 10 of compressor 12.

As shown in Figure 7, be inhaled into refrigerant (A point) in compressor 12 along how much entropy lines insulated compression in compressor 12 under the superheated vapor state.Along with refrigerant is compressed, its pressure and temperature rises, and makes refrigerant become high temperature, high pressure, high overheated steam (B point).Then refrigerant flow to heat exchanger 18.

High-pressure refrigerant steam in inflow heat exchanger 18 is cooled in order to become dry saturation vapor from superheated vapor when remaining in constant pressure in heat exchanger 18.Condensation latent heat is released, and makes refrigerant liquefy gradually, becomes thus the damp steam (E point) in the gas-liquid mixed state.Heat exchanger 18 by will be in compressor 12 heat of compressed superheated refrigerant gas isobaric be released to external agency and form refrigerant liquid.The gas phase refrigerant of emitting from compressor 12 by heat releases around heat exchanger 18 so that refrigerant is cooled and condensation (liquefaction).As carry out the result of heat exchange in heat exchanger 18, the temperature of refrigerant descends, and makes refrigerant liquefaction.Thereby refrigerant is cooled by heat release around heat exchanger 18.

The refrigerant of the damp steam state flowed out from heat exchanger 18 flows into adding in heat passage 33 so that heating-up temperature is conditioned unit 31 of heat exchange unit 30 via

refrigerant pathway

24,62,64.Carry out heat exchange in the situation that with temperature, be conditioned unit 31, the cooling and condensation of refrigerant.When refrigerant, in heat exchange unit 30 during total condensation, refrigerant forms saturated solution.In addition, refrigerant is emitted sensible heat in order to form supercooling liquid (F point).

High pressure liquid phase refrigerant by heat exchange unit 30 liquefaction flows in expansion valve 16 through refrigerant pathway 65,24.In expansion valve 16, the refrigerant of supercooling liquid status, by throttling expansion, makes the temperature and pressure of refrigerant descend when its specific enthalpy remains unchanged.As a result, refrigerant becomes in the low temperature of gas-liquid mixed state, the damp steam of low pressure (D point).

Reduce the refrigerant of temperature in expansion valve 16 in refrigerant pathway 23 inflow heat exchangers 14.The refrigerant of damp steam state flows in the pipe of heat exchanger 14.When flowing through this pipe, refrigerant via fin from extraneous air heat absorption as evaporation latent heat, and result, refrigerant evaporates remaining under the state of constant pressure.When refrigerant becomes dry saturation vapor fully, the temperature of refrigerant vapor further rises by sensible heat, and result, has formed superheated vapor (A point).Then the refrigerant of gasification be inhaled in compressor 12 via refrigerant pathway 22.The refrigerant that compressor 12 compressions come from heat exchanger 14 streams.According to this circulation, refrigerant experiences several times state variation, also i.e. compression, condensation, throttling expansion and evaporation repeatedly and continuously.

If the heating on-stream period chien shih cryogenic coolant carried out in cold period as described with reference to Figure 4 and 5 flows to the cooling channel 32 of heat exchange unit 30 so that chilling temperature is conditioned unit 31, temperature is conditioned unit 31 and is cooled to extremely low temperature.In the situation that temperature is conditioned unit 31 for the ATF cooler, preferably do not make the ATF sub-cooled, worsen and can guarantee gear lubrication thereby can suppress fuel efficiency.Therefore, when the ATF temperature is low, high-pressure refrigerant is imported to adding in heat passage 33 of heat exchange unit 30 and in order to be conditioned unit 31 with temperature, carry out heat exchange, as shown in Fig. 6 and 7, and result, can initiatively heat ATF.Therefore because the temperature that can make ATF is elevated to proper level, therefore the viscosity of ATF can not increase, and can avoid the problem not enough such as gear lubrication in friction loss increase.In addition, when hanging down, the temperature of ATF can make ATF heat up rapidly, and result, fuel efficiency can be improved and gear lubrication can be guaranteed.

As mentioned above, according to the heat-exchange device 1 of this embodiment, comprise steam compression type refrigerant cycles 10, this steam compression type refrigerant cycles is configured to carry out crew module cooling and the heating vehicle by heat exchanger 18, with the idle call air, carrying out heat exchange.Through the flow direction of the refrigerant of steam compression type refrigerant cycles 10, can use a heat exchanger 18 in cooling running and suitable temperature of regulating the idle call air in the crew module who flows into vehicle during adding heat run by utilizing cross valve 13 in cooling running and adding switching between heat run.Come to carry out heat exchange with the idle call air owing to not needing that two heat exchangers are set, therefore can realize the cost of heat-exchange device 1 and reducing of size.

Between cooling on-stream period, in the exit of expansion valve 16, refrigerant has the original temperature and pressure needed of crew module of cooling vehicle.The heat release ability of heat exchanger 14 is determined to be and makes the refrigerant can be sufficiently cooled.When refrigerant is used to when through expansion valve 16, chilling temperature is conditioned unit 31 afterwards, the ability of the cooling idle call air of heat exchanger 18 descends, thereby crew module's cooling capacity is descended.On the other hand, utilize the heat-exchange device 1 according to this embodiment, refrigerant is cooled to abundant supercooling state in heat exchanger 14, and the high-pressure refrigerant in the exit of heat exchanger 14 is used to chilling temperature and is conditioned unit 31.Therefore, can be in the situation that the ability chilling temperature of the air in not affecting cooling crew module be conditioned unit 31.

The specification of heat exchanger 14 (more specifically, the size of heat exchanger 14 or heat exchange performance) is determined to be and makes the liquid phase refrigerant temperature more required than cooling crew module in the temperature after over-heat-exchanger 14 low.The specification of heat exchanger 14 is determined to be and makes heat exchanger 14 have than in the situation that temperature is conditioned the be not cooled heat exchanger of the steam compression type refrigerant cycles used of unit 31 goes out greatly a supposition and will be conditioned by refrigerant the heat release ability of the heat that unit 31 receives from temperature.Comprise the heat exchanger 14 with these specifications heat-exchange device 1 can in the situation that the power that maintains outstanding cooling performance and do not increase compressor 12 about the crew module of vehicle suitably chilling temperature be conditioned unit 31.

Between the heating on-stream period, refrigerant is heated by the heat that is conditioned unit 31 absorptions from temperature in heat exchange unit 30, and by the heat absorbed from extraneous air, is further heated in heat exchanger 14.When refrigerant, by heat exchange unit 30 and heat exchanger 14, both heat, refrigerant can be heated in the exit of heat exchanger 14 fully overheated vapor state, and therefore temperature be conditioned unit 31 can be in the situation that maintain outstanding heating properties about the crew module of vehicle and be properly cooled.Heated by heat exchange unit 30 due to refrigerant and be effectively used to heat the crew module from the used heat that temperature is conditioned unit 31, therefore can realize the raising of the coefficient of performance, thereby the amount of power consumed for adiabatic ground compression refrigerant in compressor 12 between the heating on-stream period is reduced.

In addition, between the heating on-stream period of carrying out cold period, the high temperature by compressor 12 pressurizations, the refrigerant of high pressure is used to heat the idle call air and temperature is conditioned unit 31.Between the heating on-stream period, can be conditioned by measurement temperature such as thermistors the temperature of unit 31, so that be conditioned the temperature of unit 31 when high when temperature, can be by opening open/close valve 53 and closing open/close valve 63 and come chilling temperature to be conditioned unit 31, and be conditioned the temperature of unit 31 when low when temperature, can be by opening open/close valve 63 and closing open/close valve 53 and come heating-up temperature to be conditioned unit 31.Temperature is conditioned unit 31 and is arranged so that it is can be by the refrigerant that flows through cooling channel 32 cooling and by flowing through the refrigerant heating that adds heat passage 33, and the cryogen flow that flows through cooling channel 32 and add heat passage 33 is switched by opening and closing open/close valve 53,63.Therefore, can utilize simple configuration and the simple freely cooling or heating-up temperature of controlling to be conditioned unit 31, and result, can easily temperature be conditioned to the adjustment of unit 31 to optimum level.

In heat-exchange device 1, utilize the cooling and heating-up temperature of steam compression type refrigerant cycles 10 to be conditioned unit 31.Therefore, need to not come chilling temperature to be conditioned unit 31 by the Special cooling device such as water-circulating pump or cooling fan, and need to be such as heater heater dedicatedly come heating-up temperature to be conditioned unit 31.Therefore, can reduce to regulate the quantity that temperature is conditioned the required configuration of the temperature of unit 31, thus simplification that can the implement device configuration, and and result, can reduce the manufacturing cost of heat-exchange device 1.In addition, the power source of do not need to turn round pump, cooling fan, heater etc. is regulated the temperature that temperature is conditioned unit 31, and does not therefore need consumption of power such power source that turns round.As a result, can realize for the heating and cooling temperature is conditioned unit 31 reducing of the amount of power that consumes.

Fig. 8 is the schematic diagram illustrated according to the configuration of the heat-exchange device 1 of the second embodiment.Be according to the difference of the heat-exchange device of the heat-exchange device 1 of the second embodiment and the first embodiment, dispose the heat exchanger 15 as the 3rd heat exchanger on the refrigerant paths between heat exchange unit 30 and expansion valve 16.

By heat exchanger 15 is set, the refrigerant paths between heat exchanger 14 and expansion valve 16 is divided into the refrigerant pathway 27 of expansion valve 16 sides of the refrigerant pathway 23 of heat exchanger 14 sides of heat exchanger 15 and heat exchanger 15.Refrigerant pathway 23 is arranged in use in the path of refrigerant mobile between heat exchanger 14 and heat exchanger 15.Be conditioned first path---it comprises cooling channel 32---of the cooling system of unit 31 and the refrigerant pathway 23a parallel join of a part that forms refrigerant pathway 23 with acting on temperature.

Between cooling on-stream period, refrigerant flows through steam compression type refrigerant cycles 10 so that in turn through A point, B point, C point, D point, G point and E point, as shown in Figure 8.Thereby refrigerant circulates between compressor 12,

heat exchanger

14,15, expansion valve 16 and heat exchanger 18.Refrigerant is through by utilizing refrigerant pathway 21 to 27 to connect in turn refrigerant cycle path that compressor 12,

heat exchanger

14,15, expansion valve 16 and heat exchanger 18 form in the interior circulation of steam compression type refrigerant cycles 10.

Fig. 9 is the mollier diagram be illustrated according to the refrigerant state between the cooling on-stream period of the steam compression type refrigerant cycles 10 of the second embodiment.Transverse axis in Fig. 9 means that (unit: kJ/kg), and the longitudinal axis means the absolute pressure (unit: MPa) of refrigerant for the specific enthalpy of refrigerant.The saturated vapor line that curve in figure is refrigerant and saturated liquidus.Fig. 9 illustrates that refrigerant flows into refrigerant pathways 23 in via heat exchanger 14 from compressor 12 at refrigerant, chilling temperature is conditioned unit 31, returns to refrigerant pathway 23, via in heat exchanger 15 inflow refrigerant pathways 27 and then via expansion valve 16 and heat exchanger 18, return to the thermodynamic state of each point (that is, A, B, C, D, G and E point) of the steam compression type refrigerant cycles 10 of compressor 12.

Identical with the steam compression type refrigerant cycles of the first embodiment except the system that extends to expansion valve 16 from heat exchanger 14 according to the steam compression type refrigerant cycles 10 of the second embodiment.The refrigerant state of more specifically, ordering to B with the A point via the E point from the D point on the mollier diagram shown in Fig. 2 is identical with the refrigerant state of ordering to B via E point and A point from the G point the mollier diagram shown in Fig. 9.Therefore, the refrigerant state of from B point to G ordering unique according to the steam compression type refrigerant cycles 10 of the second embodiment hereinafter will be described.

By compressor 12 adiabatic be compressed into the superheated vapor of high temperature, high pressure refrigerant (B point) in heat exchanger 14, be cooled.As a result, refrigerant is emitted sensible heat in order to become dry saturation vapor from superheated vapor remaining under the state of constant pressure.Then condensation latent heat is released, and makes refrigerant liquefy gradually, becomes thus the damp steam in the gas-liquid mixed state, and, when the refrigerant total condensation, refrigerant becomes saturated solution (C point).

The refrigerant of the saturated solution state flowed out from heat exchanger 14 flows in heat exchange unit 30 through refrigerant pathway 52,54.In heat exchange unit 30, to the liquid cryogen heat release in condensation in over-heat-exchanger 14, chilling temperature is conditioned unit 31 by this.Refrigerant carries out heat exchange and is heated by with temperature, being conditioned unit 31, and result, and the aridity of refrigerant increases.When receiving from temperature, refrigerant is conditioned the latent heat of unit 31 and while standing partial gasification, refrigerant becomes the damp steam (D point) that and saturated solution and saturated vapor mixes mutually.

Refrigerant is then in inflow heat exchanger 15.The damp steam of refrigerant carries out heat exchange with extraneous air in heat exchanger 15 so that condensation again, and, when total condensation, refrigerant forms saturated solution.In addition, refrigerant is emitted sensible heat in order to form supercooling liquid (G point).Then refrigerant pass through expansion valve 16, in order to form the damp steam (E point) of low temperature, low pressure.

In steam compression type refrigerant cycles 10, the high-pressure refrigerant of emitting from compressor 12 is by heat exchanger 14 and heat exchanger 15 both condensations.Abundant when cooling in heat exchanger 15 when refrigerant, refrigerant has the original required temperature and pressure of crew module of cooling vehicle in the exit of expansion valve 16.Therefore, the heat received from outside in the time of can making refrigerant be in heat exchanger 18 to evaporate is enough large.Be specified to and make it possible to abundant cooling refrigerant in this way by the heat release ability by heat exchanger 15, under the prerequisite of the ability of air that can be in not affecting cooling crew module, chilling temperature is conditioned unit 31.As a result, can guarantee reliably that chilling temperature is conditioned the ability of unit 31 and cooling crew module's ability.

In the steam compression type refrigerant cycles 10 according to the first embodiment, heat exchanger 14 is configured between compressor 12 and expansion valve 16, make between cooling on-stream period, must be carried out being conditioned with crew module's cooling and temperature by heat exchanger 14 the cooling corresponding heat exchange amount of unit 31.Therefore, refrigerant must be further cooling from the saturated solution state in heat exchanger 14, until refrigerant possesses predetermined supercooling degree.When the refrigerant in the supercooling liquid status is cooled, the temperature of refrigerant approaches atmospheric temperature, thereby the cooling effectiveness of refrigerant is reduced, and therefore must increase the capacity of heat exchanger 14.As a result, the size of heat exchanger 14 increases, and this is disadvantageous for vehicle-mounted heat-exchange device 1.On the other hand, when the size that reduces heat exchanger 14 is installed to be conducive to vehicle, the heat release ability of heat exchanger 14 descends.As a result, possibly can't fully be reduced in the temperature of refrigerant in exit of expansion valve 16, thereby make cooling crew module's scarce capacity.

Yet, by the steam compression type refrigerant cycles 10 according to the second embodiment, between compressor 12 and expansion valve 16, with two-step way

configuration heat exchanger

14,15, and be arranged between heat exchanger 14 and heat exchanger 15 with the heat exchange unit 30 that acts on temperature and be conditioned the cooling system of unit 31.As shown in Figure 9, refrigerant only need be cooled to the saturated solution state in heat exchanger 14.Be conditioned unit 31 reception evaporation latent heats from temperature after, partly the refrigerant of the damp steam state of gasification is then again cooling heat exchanger 15.The state of refrigerant changes under steady temperature, until the refrigerant of damp steam state total condensation become saturated solution.In addition, heat exchanger 15 is cooled to refrigerant the required supercooling degree of crew module of cooling vehicle.Therefore, with the first embodiment, compare, needn't increase the supercooling degree of refrigerant, and capacity that can corresponding reduction heat exchanger 14,15.Therefore, cooling crew module's ability can be guaranteed, and the size of

heat exchanger

14,15 can be reduced.As a result, in vehicle, install being suitable for the heat-exchange device 1 of this acquisition is enough little.

When the refrigerant chilling temperature in heat exchanger 14 inflow heat exchange units 30 is conditioned unit 31, refrigerant is heated by the heat that is conditioned unit 31 receptions from temperature.Be heated to saturated with vapor temperature or above and while making refrigerant be gasified totally in heat exchange unit 30 when refrigerant, the heat exchange amount that refrigerant and temperature are conditioned between unit 31 reduces, and makes temperature be conditioned unit 31 and no longer can be increased by the pressure loss that cooling and refrigerant produces when flowing through pipe effectively.Therefore, refrigerant is preferably sufficiently cooled in heat exchanger 14, to guarantee refrigerant, after chilling temperature is conditioned unit 31, can not be gasified totally.

More specifically, make to approach saturated solution at the refrigerant state in the exit of heat exchanger 14, so that usually have the refrigerant state on saturated liquidus in the exit of heat exchanger 14.When heat exchanger 14 is provided the ability of abundant cooling refrigerant in this way, heat exchanger 14 improves the heat release ability that exceeds heat exchanger 15 for the heat release ability from the refrigerant heat release.By abundant cooling refrigerant in the heat exchanger 14 thering is larger heat release ability, refrigerant can remain in the damp steam state after being heated being conditioned unit 31 from temperature, avoid thus refrigerant and temperature to be conditioned the minimizing of the heat exchange amount between unit 31, and result, can be effectively and fully chilling temperature be conditioned unit 31.After chilling temperature is conditioned unit 31, the refrigerant of damp steam state again effectively is cooled to the supercooling liquid status a little less than saturation temperature in heat exchanger 15.Therefore, by the heat-exchange device 1 provided at this, can guarantee cooling crew module's ability and the ability that chilling temperature is conditioned unit 31.

Figure 10 is the schematic diagram illustrated according to the state be switched in cross valve 13 of the heat-exchange device 1 of the second embodiment.Comparison diagram 8 and 10, cross valve 13 is half-twist, thus switching for from the outlet of compressor 12, flow into refrigerant in cross valve 13 along it from cross valve 13 paths that emit.Between the cooling on-stream period shown in Fig. 8, the refrigerant compressed by compressor 12 flows to heat exchanger 14 from compressor 12.On the other hand, between the heating on-stream period shown in Figure 10, the refrigerant compressed by compressor 12 flows to heat exchanger 18 from compressor 12.

Between the heating on-stream period, refrigerant flows through steam compression type refrigerant cycles 10 so that in turn through A point, B point, E point, G point, D point and C point, as shown in figure 10.Thereby refrigerant circulates between compressor 12, heat exchanger 18, expansion valve 16 and heat exchanger 15,14.Refrigerant is through by utilizing refrigerant pathway 21 to 27 to connect in turn refrigerant cycle path that compressor 12, heat exchanger 18, expansion valve 16 and

heat exchanger

15,14 form in the interior circulation of steam compression type refrigerant cycles 10.

Figure 11 is the mollier diagram be illustrated according to the refrigerant state between the heating on-stream period of the steam compression type refrigerant cycles 10 of the second embodiment.Transverse axis in Figure 11 means that (unit: kJ/kg), and the longitudinal axis means the absolute pressure (unit: MPa) of refrigerant for the specific enthalpy of refrigerant.The saturated vapor line that curve in figure is refrigerant and saturated liquidus.Figure 11 illustrate refrigerant refrigerant via heat exchanger 18, expansion valve 16 and heat exchanger 15 from compressor 12 flow in refrigerant pathways 23, chilling temperature is conditioned unit 31, return to refrigerant pathway 23 and then via heat exchanger 14, return to the thermodynamic state of each point (that is, A, B, E, G, D and C point) of the steam compression type refrigerant cycles 10 of compressor 12.

Identical with the steam compression type refrigerant cycles 10 of the first embodiment except the system that extends to heat exchanger 14 from expansion valve 16 according to the steam compression type refrigerant cycles 10 of the second embodiment.The refrigerant state of more specifically, ordering to D with the E point via the B point from the A point on the mollier diagram shown in Fig. 5 is identical with the refrigerant state of ordering to G via B point and E point from the A point the mollier diagram shown in Figure 11.Therefore, the refrigerant state of from G point to A ordering unique according to the steam compression type refrigerant cycles 10 of the second embodiment hereinafter will be described.

The refrigerant (G point) of lowering the temperature by expansion valve 16 is in refrigerant pathway 27 inflow heat exchangers 15.The refrigerant of damp steam state flows in the pipe of heat exchanger 15.When flowing through this pipe, refrigerant via fin from extraneous air heat absorption as evaporation latent heat, and result, refrigerant evaporates remaining under the state of constant pressure.Then refrigerant be heated by heat exchanger 15, with extraneous air, carrying out heat exchange, and the aridity of refrigerant increases by this.When refrigerant receives latent heat in heat exchanger 15, the one partial gasification, thus make the ratio of the saturated vapor in the refrigerant of damp steam state increase (D point).

The refrigerant of the damp steam state of emitting from heat exchanger 15 flows in the cooling channel 32 of heat exchange unit 30 through

refrigerant pathway

23,55, and chilling temperature is conditioned unit 31.In heat exchange unit 30, heat is released to the refrigerant of the damp steam state mixed mutually with saturated solution and saturated vapor, and chilling temperature is conditioned unit 31 by this.Refrigerant carries out heat exchange and is heated by with temperature, being conditioned unit 31, and result, and the aridity of refrigerant increases.When refrigerant is conditioned unit 31 and receives latent heat from temperature, the one partial gasification, thus make the ratio of the saturated vapor in the refrigerant of damp steam state further increase (C point).

refrigerant pathway

54,52, and then in inflow heat exchanger 14.The refrigerant of damp steam state flows in the pipe of heat exchanger 14.When flowing through this pipe, refrigerant via fin from extraneous air heat absorption as evaporation latent heat, and result, refrigerant evaporates remaining under the state of constant pressure.When refrigerant becomes dry saturation vapor fully, the temperature of refrigerant vapor further rises by sensible heat, and result, and refrigerant vapor becomes superheated vapor (A point).

Between the heating on-stream period, refrigerant is heated by the heat absorbed from extraneous air in two

heat exchangers

14,15, and then in heat exchange unit 30, by the heat that is conditioned unit 31 absorptions from temperature, further is heated.By at heat exchange unit 30 and

heat exchanger

14,15, adding hot refrigerant in both, refrigerant can be heated in the exit of heat exchanger 14 fully overheated vapor state, and therefore can maintain the crew module about vehicle in outstanding heating properties suitably chilling temperature and be conditioned unit 31.Heated by heat exchange unit 30 due to refrigerant and be effective to heat the crew module from the used heat that temperature is conditioned unit 31, therefore can be reduced in the amount of power consumed for adiabatic ground compression refrigerant in compressor 12 between the heating on-stream period.

Figure 12 is the schematic diagram that the heat-exchange device 1 when temperature according to a second embodiment of the present invention is conditioned unit 31 and is heated is shown.Be similar to the first embodiment, by the opening/closing state that switches open/

close valve

53,63, make open/close valve 53 close and open/close valve 63 is opened, set up that refrigerant flows through heating path 33 but the state that do not flow through cooling channel 32.Now, heat is delivered to temperature and is conditioned unit 31 from flowing through the refrigerant that adds heat passage 33, and result, and temperature is conditioned unit 31 and is heated.

Figure 13 is the mollier diagram that the state of the refrigerant used in the steam compression type refrigerant cycles 10 according to the second embodiment when temperature is conditioned unit 31 and is heated is shown.Transverse axis in Figure 13 means that (unit: kJ/kg), and the longitudinal axis means the absolute pressure (unit: MPa) of refrigerant for the specific enthalpy of refrigerant.The saturated vapor line that curve in figure is refrigerant and saturated liquidus.Figure 13 illustrate refrigerant refrigerant via heat exchanger 18 from compressor 12 flow in refrigerant pathways 24, heating-up temperature is conditioned unit 31, return to refrigerant pathway 24 and then via expansion valve 16 and

heat exchanger

15,14, return to the thermodynamic state of each point (that is, A, B, E, F, G and D point) of the steam compression type refrigerant cycles 10 of compressor 12.

Identical with the steam compression type refrigerant cycles of the first embodiment except the system that extends to heat exchanger 14 from expansion valve 16 according to the steam compression type refrigerant cycles 10 of the second embodiment.The refrigerant state of more specifically, ordering to D with the F point via B, E from the A point on the mollier diagram shown in Fig. 7 is identical with the refrigerant state of ordering to G via B, E and F point from the A point the mollier diagram shown in Figure 13.Therefore, the refrigerant state of from G point to A ordering unique according to the steam compression type refrigerant cycles 10 of the second embodiment hereinafter will be described.

The refrigerant (G point) of lowering the temperature by expansion valve 16 is in refrigerant pathway 27 inflow heat exchangers 15.The refrigerant of the damp steam state mixed mutually with saturated solution and saturated vapor flows in the pipe of heat exchanger 15.When flowing through this pipe, refrigerant via fin from extraneous air heat absorption as evaporation latent heat, and result, refrigerant evaporates remaining under the state of constant pressure.Then refrigerant be heated by heat exchanger 15, with extraneous air, carrying out heat exchange, and the aridity of refrigerant increases by this.When refrigerant receives latent heat in heat exchanger 15, the one partial gasification, thus make the ratio of the saturated vapor in the refrigerant of damp steam state increase (D point).

The refrigerant of the damp steam state of emitting from heat exchanger 15 is in refrigerant pathway 23 inflow heat exchangers 14.The refrigerant of the damp steam state mixed mutually with saturated solution and saturated vapor flows in the pipe of heat exchanger 14.When flowing through this pipe, refrigerant via fin from extraneous air heat absorption as evaporation latent heat, and result, refrigerant evaporates remaining under the state of constant pressure.When refrigerant becomes dry saturation vapor fully, the temperature of refrigerant vapor further rises by sensible heat, and result, and refrigerant vapor becomes superheated vapor (A point).

Between the heating on-stream period of carrying out cold period, the idle call air is heated, and by high-pressure refrigerant being flowed in heat exchange unit 30 and being conditioned with temperature that unit 31 carries out heat exchange and heating-up temperature is conditioned unit 31.In the situation that temperature is conditioned unit 31 for the ATF cooler, can initiatively heat ATF so that ATF is warmed up to proper level.As a result, the viscosity of ATF can not increase, and therefore can avoid the problem not enough such as gear lubrication in friction loss increase.Through after expansion valve 16, the refrigerant of low temperature, low pressure respectively by two

heat exchangers

15,14 with two-step heating, and therefore can reduce

heat exchanger

14,15 heat-exchange capacity separately.Therefore, can correspondingly reduce the size of

heat exchanger

14,15, and result, install in vehicle being suitable for the heat-exchange device 1 of this acquisition is enough little.

Figure 14 is the schematic diagram illustrated according to the configuration of the heat-exchange device 1 of the 3rd embodiment.According to the difference of the heat-exchange device of the heat-exchange device 1 of the 3rd embodiment and the first and second embodiment, be, replacement is set as

refrigerant pathway

52,54 on the open/close valve 53 of connected state or non-connected state, is provided with expansion valve 56 as second pressure reducer different from the first pressure reducer (expansion valve 16) on the refrigerant paths between heat exchanger 14 and heat exchange unit 30.Be similar to expansion valve 16, expansion valve 56 expands and reduces the temperature and pressure of refrigerant by the high pressure liquid phase refrigerant that makes to emit from heat exchanger 14.Heat-exchange device 1 also comprises the refrigerant pathway 57 as the refrigerant paths of walking around expansion valve 56, and is arranged in refrigerant pathway 57 cryogen flow is switched to the open/close valve 58 of refrigerant pathway 57.

Between cooling on-stream period, as shown in figure 14, open/close valve 58 cuts out.Therefore, in heat exchanger 14, the refrigerant of condensation flows to heat exchange unit 30 through refrigerant pathway 52, expansion valve 56 and refrigerant pathway 54.In inflow heat exchange unit 30, so that the refrigerant of process cooling channel 32 is by being conditioned unit 31 heat absorptions from temperature, chilling temperature is conditioned unit 31.Therefore, heat exchange unit 30 utilizes from heat exchanger 14 and emits and come chilling temperature to be conditioned unit 31 by the low temperature of expansion valve 56 decompressions, the refrigerant of low pressure.

Figure 15 is the mollier diagram be illustrated according to the refrigerant state between the cooling on-stream period of the steam compression type refrigerant cycles 10 of the 3rd embodiment.Transverse axis in Figure 15 means that (unit: kJ/kg), and the longitudinal axis means the absolute pressure (unit: MPa) of refrigerant for the specific enthalpy of refrigerant.The saturated vapor line that curve in figure is refrigerant and saturated liquidus.Figure 15 illustrates refrigerant and flows in refrigerant pathways 52, expansion valve 56 and flow through the thermodynamic state of each point (that is, A, B, H, C, D, G and E) that refrigerant pathway 54, chilling temperature are conditioned unit 31 and then from refrigerant pathway 55, in the porch of heat exchanger 15, return to the steam compression type refrigerant cycles 10 of refrigerant pathway 23 after expansion from refrigerant pathway 23 in the exit of heat exchanger 14 at refrigerant.

Identical with the steam compression type refrigerant cycles of the second embodiment except the system that extends to expansion valve 16 from heat exchanger 14 according to the steam compression type refrigerant cycles 10 of the 3rd embodiment.The refrigerant state of more specifically, ordering to C with the B point via the A point from the E point on the mollier diagram shown in Fig. 9 is identical with the refrigerant state of ordering to H via A point and B point from the E point the mollier diagram shown in Figure 15.Therefore, the refrigerant state of from H point to E ordering unique according to the steam compression type refrigerant cycles 10 of the 3rd embodiment hereinafter will be described.

In heat exchanger 14, the refrigerant (H point) of liquefaction flows in expansion valve 56 through refrigerant pathway 23,52.In expansion valve 56, the refrigerant of saturated solution form, by throttling expansion, makes the temperature and pressure of refrigerant descend when its specific enthalpy remains unchanged.As a result, refrigerant becomes the damp steam (C point) mixed mutually with saturated solution and saturated vapor.The refrigerant that reduces temperature in expansion valve 56 flows in the cooling channel 32 of heat exchange units 30 also chilling temperature and is conditioned unit 31 via refrigerant pathway 54.Refrigerant carries out heat exchange and is heated by with temperature, being conditioned unit 31, and result, and the aridity of refrigerant increases.Refrigerant is conditioned unit 31 from temperature and receives latent heat and stand partial gasification, thereby makes the ratio of the saturated vapor in the refrigerant of damp steam state increase (D point).

Refrigerant is then in inflow heat exchanger 15.The damp steam of refrigerant is condensation again in heat exchanger 15, and, when total condensation, refrigerant forms saturated solution.In addition, refrigerant is emitted sensible heat in order to form supercooling liquid (G point).Then refrigerant pass through expansion valve 16, and the refrigerant of supercooling liquid status by throttling expansion, makes the temperature and pressure of refrigerant descend when its specific enthalpy remains unchanged in expansion valve 16.As a result, refrigerant forms in the low temperature of gas-liquid mixed state, the damp steam of low pressure (some E).

In the heat-exchange device 1 according to the 3rd embodiment, can utilize the refrigerant chilling temperature between cooling on-stream period expanded by expansion valve 56 to be conditioned unit 31 in order to reduce temperature, and therefore more effectively chilling temperature be conditioned unit 31.By being that expansion valve 56 is selected optimum specifications, can regulate by expectation the temperature that chilling temperature is conditioned the refrigerant of unit 31 by heat exchange unit 30.Therefore, can come chilling temperature to be conditioned unit 31 by supply with the refrigerant with lower temperature that is more suitable for being conditioned in chilling temperature unit 31 to heat exchange unit 30.

Figure 16 is the schematic diagram illustrated according to the state be switched in cross valve of the heat-exchange device of the 3rd embodiment.When utilizing heat-exchange device 1 according to the 3rd embodiment to be added heat run, expansion valve 56 cuts out (being set in aperture 0%) fully and open/close valve 58 is opened.Therefore, refrigerant flows through steam compression type refrigerant cycles 10 so that in turn through A point, B point, E point, G point, D point and C point, as shown in figure 16.Thereby refrigerant circulates between compressor 12, heat exchanger 18, expansion valve 16 and

heat exchanger

15,14.

Now, at its state, in the mode to shown in Figure 11, similar mode circulates through steam compression type refrigerant cycles 10 when changing refrigerant.Therefore, be similar to the second embodiment, refrigerant is by heat exchange unit 30 and

heat exchanger

14,15 both heating, make refrigerant can be heated in the exit of heat exchanger 14 fully overheated vapor state, and therefore temperature be conditioned unit 31 can be in the situation that maintain outstanding heating properties about the crew module of vehicle and be properly cooled.

Figure 17 is the schematic diagram that the heat-exchange device 1 when the temperature according to the 3rd embodiment is conditioned unit 31 and is heated is shown.When utilizing heat-exchange device 1 according to the 3rd embodiment heating-up temperature is conditioned unit 31 between the heating on-stream period of carrying out cold period, expansion valve 56 cuts out (being set in aperture 0%) fully, and open/close valve 58 cuts out, and open/close valve 63 is opened.Therefore, refrigerant flows through steam compression type refrigerant cycles 10 in order to pass through in turn A, B, E, F, G and D point, as shown in figure 17.Thereby refrigerant circulates between compressor 12, heat exchanger 18, expansion valve 16 and

heat exchanger

15,14.

Now, at its state, in the mode to shown in Figure 13, similar mode circulates through steam compression type refrigerant cycles 10 when changing refrigerant.Therefore, be similar to the second embodiment, between the heating on-stream period of carrying out cold period, can heat the idle call air, and can by high-pressure refrigerant is imported, heat exchange unit 30 is interior comes heating-up temperature to be conditioned unit 31.In the situation that temperature is conditioned unit 31 for the ATF cooler, can initiatively heat ATF, ATF can be warmed up to proper level by this.As a result, the viscosity of ATF can not increase, and therefore can avoid the problem not enough such as gear lubrication in friction loss increase.

Note, in the first to the 3rd embodiment, utilize the ATF cooler to describe as example the heat-exchange device 1 that adjustment that the temperature that will be arranged in vehicle is conditioned unit is optimum temperature.Yet, stand thermoregulator temperature by heat-exchange device 1 according to the present invention and be conditioned unit 31 and be not limited to be arranged on the ATF cooler in vehicle, and can replace with coming cooling or any device of heating or the heating part of this device according to the various conditions such as external air temperature.

Above described embodiments of the invention, but the configuration of each embodiment can suitably combine.In addition, embodiment disclosed herein is the example about all main points, and therefore should not be considered restriction.Scope of the present invention is limited by scope rather than the above description of claim, and intention comprise with the scope of claim and this scope in the definition that is equal to of all modification.

Heat-exchange device according to the present invention is particularly suitable for utilizing the steam compression type refrigerant cycles of the vehicle interior of heating and cooling vehicle to regulate needs the temperature such as the ATF cooler cooling or heating to be conditioned the temperature of unit.

Claims

1. a heat-exchange device, described heat-exchange device is conditioned between unit and carries out heat exchange in refrigerant and temperature, and described heat-exchange device comprises:

Compressor, the described refrigerant of described compressor compresses is in order to make described refrigerant circulate through described heat-exchange device;

The first heat exchanger, described the first heat exchanger carries out heat exchange between described refrigerant and extraneous air;

The first pressure reducer, described the first pressure reducer makes described refrigerant decompression;

The second heat exchanger, described the second heat exchanger carries out heat exchange between described refrigerant and idle call air;

The first path, described the first path forms for described refrigerant mobile path between described the first heat exchanger and described the first pressure reducer; With

Alternate path, described alternate path forms for described refrigerant mobile path between described the first pressure reducer and described the second heat exchanger,

Wherein, described temperature is conditioned cell location and becomes and can carry out heat exchange and can carry out heat exchange with the described refrigerant that flows through described alternate path with the described refrigerant that flows through described the first path.

2. heat-exchange device according to claim 1 also comprises:

Cross valve, described cross valve switches the cryogen flow from described compressor to described the first heat exchanger and the cryogen flow from described compressor to described the second heat exchanger.

3. heat-exchange device according to claim 1 and 2 also comprises:

Three-way, described three-way on the refrigerant paths between described the first heat exchanger and described the first pressure reducer with described the first path parallel join; With

The first flow control valve, described first flow control valve is regulated the flow of the described refrigerant that flows through described the first path and is flow through the flow of the described refrigerant of described three-way.

4. heat-exchange device according to claim 3 also comprises:

The four-way road, described four-way road on the refrigerant paths between described the first pressure reducer and described the second heat exchanger with described alternate path parallel join; With

The second control valve, described second control valve is regulated the flow of the described refrigerant that flows through described alternate path and is flow through the flow of the described refrigerant on described four-way road.

5. according to the described heat-exchange device of claim 3 or 4, also comprise:

The first open/close valve, described the first path is opened and sealed to the described first open/close valve.

6. heat-exchange device according to claim 5 also comprises:

The second open/close valve, described alternate path is opened and sealed to the described second open/close valve.

7. heat-exchange device according to claim 6, wherein, the described second open/close valve cuts out when the described first open/close valve is opened, and the described second open/close valve is opened when the described first open/close valve cuts out.

8. according to the described heat-exchange device of any one in claim 1 to 4, also comprise:

The second pressure reducer, described the second pressure reducer described the first heat exchanger and described temperature be conditioned between unit be arranged on described the first path in order to make described refrigerant decompression.

9. heat-exchange device according to claim 8 also comprises:

The five-way road, described five-way road is in a part that forms described the first path and through described temperature, be conditioned on the path of unit and described the first heat exchanger and path parallel join through described the second pressure reducer; With

The 3rd open/close valve, described the 3rd open/close valve is arranged in described five-way road in order to open and seal described five-way road.