CN103201580A

CN103201580A - Heat exchanger

Info

Publication number: CN103201580A
Application number: CN201180054056XA
Authority: CN
Inventors: 加藤吉毅
Original assignee: Denso Corp
Current assignee: Denso Corp
Priority date: 2010-11-09
Filing date: 2011-11-07
Publication date: 2013-07-10
Anticipated expiration: 2031-11-07
Also published as: DE112011103727T5; CN103201580B; JP5413433B2; US20130240185A1; WO2012063454A1; JP2012117802A

Abstract

Refrigerant tubes (61) and cooling medium tubes (71) are alternately disposed and stacked between a refrigerant header tank (62) and a cooling medium header tank (72), the refrigerant tubes (61) each comprising a refrigerant-side turn section (61e) for changing the direction of flow of a refrigerant, the cooling medium tubes (71) each comprising a cooling medium-side turn section (71e) for changing the direction of flow of cooling water for an electric motor (MG) for traveling. Outer fins are disposed in an outside-air path formed between each of the refrigerant tubes (61) and each of cooling water tubes (43a), which are adjacent to each other. The refrigerant-side turn sections (61e) are disposed at positions closer to the cooling medium header tank (72) than the refrigerant header tank (62), and the cooling medium-side turn sections (71e) are disposed at positions closer to the refrigerant header tank (62) than the cooling medium header tank (72).

Description

Heat exchanger

The cross reference of related application

The application based on and advocate the rights and interests of the priority of Japanese patent application 2010-251119 number of filing an application on November 9th, 2010 and the Japanese patent application of filing an application on October 24th, 2011 2011-233083 number, the disclosure of described application is by reference in this merging.

Technical field

The present invention relates to a kind of can be between three kinds of fluids the composite heat exchanger of heat-shift.

Background technology

Traditionally, known can be between three kinds of fluids the composite heat exchanger of heat-shift.For example, patent documentation 1 disclose a kind of can be between the cold-producing medium of outdoor air (extraneous air) and refrigerant cycle apparatus and cold-producing medium and be used for the composite heat exchanger of heat-shift between the cooling agent of cooled engine.

Particularly, disclosed heat exchanger comprises stacked a plurality of linear refrigerant pipe in the patent documentation 1, and each refrigerant pipe all has two ends that are connected to for the refrigerant case of collection or assignment system cryogen.Heat exchanger also comprises heat pipe, and each heat pipe all has an end that is connected to for the cooling fluid tank of circulating coolant, and is parallel to stacked refrigerant pipe and is arranged between the described refrigerant pipe.In addition, be used for promoting that the fin of heat exchange is arranged in the outside air opening that is formed between refrigerant pipe and the heat pipe.Refrigerating circulatory device in the patent documentation 1 adopts this composite heat exchanger as the evaporimeter of heat (for example, the used heat of the engine) vaporized refrigerant that is used for heat by absorbing extraneous air at cold-producing medium and cooling agent.At this moment, the used heat of the engine that shifts from heat pipe can be used for suppressing the frosting of heat exchanger.

[correlation technique document]

[patent documentation]

[patent documentation 1]

Japanese unexamined patent discloses 11-157326 number

In order in the heat exchanger of patent documentation 1, to obtain heat exchange between cold-producing medium and the extraneous air and the heat exchange between cold-producing medium and the cooling agent as mentioned above, refrigerant case and cooling fluid tank are adjacent one another are along the flow direction of extraneous air, and heat pipe makes heat pipe be arranged between the linear refrigerant pipe that extends near the cooling fluid tank bending.

Yet refrigerant case and cooling fluid tank cause whole heat exchanger to increase along the size of flow of external air direction along flow of external air direction layout adjacent one another are.In addition, the heat exchanger of patent documentation 1 must use the heat pipe near the complicated shape of cooling fluid tank bending, thereby causes the productivity ratio of heat exchanger low.

Summary of the invention

Considered that above problem finished the present invention, and the objective of the invention is to improve can be between three kinds of fluids the productivity ratio of the heat exchanger of heat-shift.

According to a first aspect of the invention, a kind of heat exchanger comprises: first heat exchange department, described first heat exchange department comprises a plurality of first pipes that first fluid flows through and extends to collect or distribute first case of the first fluid that flows through first pipe at the stacked direction of first pipe that first heat exchange department is suitable at first fluid and heat-shift between the 3rd mobile around first pipe fluid; With second heat exchange department, described second heat exchange department comprises a plurality of second pipes that second fluid flows through and extends to collect or distribute second case of second fluid that flows through second pipe at the stacked direction of second pipe that second heat exchange department is suitable at second fluid and heat-shift between the 3rd mobile around second pipe fluid.First pipe and second pipe are arranged between first the case and second the case, in first pipe at least one is arranged between second pipe, in second pipe at least one is arranged between first pipe, be formed on the 3rd fluid passage that space boundary the 3rd fluid between first pipe and second pipe flows through, and outer fin is arranged in the 3rd fluid passage to promote first heat exchange department and the heat exchange between the two of second heat exchange department, can carry out the heat transmission between the first fluid that flows through first pipe and second fluid that flows through second pipe simultaneously.In addition, first pipe is provided with first turning part for the flow direction that changes first fluid, second pipe is provided with second turning part for the flow direction that changes second fluid, first turning part is oriented to than first case close more second case, and second turning part is oriented to than second the case more near first case.

Therefore, can be via first pipe and the outer fin heat-shift between first fluid and the 3rd fluid.Can also be via second pipe and the outer fin heat-shift between second fluid and the 3rd fluid.Further can be via outer fin heat-shift between first fluid and second fluid.Therefore, can between three kinds of fluids, carry out heat exchange.

First pipe and second pipe are arranged between first the case and second the case, and the 3rd fluid passage is formed in the space between first pipe and second pipe, make win case and second case less than the flow direction layout along the 3rd fluid.Therefore, can prevent that whole heat exchanger from increasing along the size of the flow direction of the 3rd fluid.

First turning part of first pipe is oriented to than first case more close second case, and second turning part of second pipe is oriented to than second case more close first case, the pipe of winning can be had with second with first case connection manage shape identical with second case be connected or that be equal to.

Therefore, heat exchanger of the present disclosure can improve under the situation that does not increase size can be between three kinds of fluids the productivity ratio of the heat exchanger of heat-shift.Not only represent to have the fluid of different qualities or composition as term used herein " three kinds of fluids ", even and expression when these fluids have identical characteristic or composition and aspect temperature or state (for example gas phase or liquid phase) different fluids.Therefore, first to the 3rd fluid is not limited to the fluid with different qualities or composition.

According to a second aspect of the invention, be introduced in the first fluid in first heat exchange department temperature can be introduced in second heat exchange department in the temperature of second fluid different, and outer fin can be arranged in the space that is formed between first pipe and second pipe and other first pipe that is adjacent and second pipe.

When the temperature of the first fluid that is introduced in first heat exchanger is different from the temperature that is introduced in second fluid in second heat exchanger, the thermal strain that produces in first pipe (amount of thermal expansion) is different from the thermal strain that produces in second pipe, and this may change the size of first pipe and second pipe.In this case, outer fin promotes the heat exchange between each fluid, thereby reduces the temperature difference between first fluid and second fluid to alleviate the difference of the thermal strain between (reducing) first pipe and second pipe.Therefore, the destruction that can suppress heat exchanger.

As term used herein " be formed on first pipe and second pipe and other first pipe of being adjacent and second pipe between the space " expression be formed on first pipe and and as described between adjacent another of first pipe first pipe or second pipe and second pipe and and as described in second manage adjacent first manage or another second pipe between the space.

The movement in heat exchanger as term used herein " introducing " or " outflow " expression cold-producing medium, and term used herein " inflow " or the movement of " outflow " expression cold-producing medium in each pipe.

According to a third aspect of the invention we, each in first pipe and second pipe can be fixed to first the case and second case.

Because first pipe and second pipe are fixed to first the case and second case, the mechanical strength of whole heat exchanger is increased.Further, easily secure is arranged on the outer fin in the 3rd fluid passage that arranges between first pipe and second pipe.

According to a forth aspect of the invention, first fluid in being introduced in first heat exchange department and be introduced in a fluid that has higher temperature in second fluid in second heat exchange department and be defined as the high temperature side fluid, the high temperature side pipe that flows through of high temperature fluid in first pipe and second pipe be defined as high temperature side pipe upstream portion with respect to corresponding one upstream portion in first turning part and second turning part, and when the high temperature side pipe that flows through of high temperature fluid in first pipe and second pipe with respect to first turning part and second turning part in corresponding one downstream sidepiece when being defined as high temperature side pipe downstream portion, the temperature of the 3rd fluid can be lower than the temperature of high temperature side fluid, and at least one the high temperature side pipe upstream portion in the high temperature side pipe can be positioned at upstream side along the flow direction of described the 3rd fluid with respect to high temperature side pipe downstream portion.

The upstream side of fluid stream that therefore, can be in the high temperature side pipe guarantees that the temperature difference between high temperature side fluid and the 3rd fluid is with the amount of increase heat dissipation.Therefore, the temperature difference that can reduce between first fluid and second fluid is poor with the thermal strain that alleviates between first pipe and second pipe, thus the destruction that can suppress heat exchanger.

According to a fifth aspect of the invention, first fluid in being introduced in first heat exchange department and be introduced in a fluid that has lower temperature in second fluid in second heat exchange department and be defined as the low temperature side fluid, the low temperature side pipe that passes through of cry-fluid flow in first pipe and second pipe be defined as low temperature side pipe upstream portion with respect to corresponding one upstream portion in first turning part and second turning part, and when corresponding one the downstream sidepiece with respect in first turning part and second turning part of the low temperature side pipe that passes through of cry-fluid flow in first pipe and second pipe is defined as low temperature side pipe downstream portion, the temperature of the 3rd fluid can be lower than the temperature of low temperature side fluid, and at least one the low temperature side pipe upstream portion in the low temperature side pipe can be positioned at upstream side along the flow direction of the 3rd fluid with respect to low temperature side pipe downstream portion.The upstream side of fluid stream that therefore, can be in the low temperature side pipe guarantees that the temperature difference between low temperature side fluid and the 3rd fluid is with the amount of increase heat dissipation.Therefore, the temperature difference that can reduce between first fluid and second fluid is poor with the thermal strain that alleviates between first pipe and second pipe, thus the destruction that can suppress heat exchanger.

According to a sixth aspect of the invention, the temperature of the 3rd fluid can be lower than the first fluid that is introduced in first heat exchange department and be introduced in the temperature of a fluid that has higher temperature in second fluid in second heat exchange department and can be higher than the temperature of another fluid with lower temperature.

Therefore, the temperature of the high temperature side fluid in the first fluid in the heat exchanger and second fluid is lowered, and the temperature of low temperature side fluid increases simultaneously, thereby can reduce the temperature difference between first fluid and second fluid.Therefore, can reduce the difference of the thermal strain between each pipe to suppress the destruction of heat exchanger effectively.

According to a seventh aspect of the invention, when first pipe is defined as the first pipe upstream portion with respect to the upstream portion of first turning part, first pipe is defined as the first pipe downstream portion with respect to the downstream sidepiece of first turning part, second pipe is defined as the second pipe upstream portion with respect to the upstream portion of second turning part, and second pipe when being defined as the second pipe downstream portion with respect to the downstream sidepiece of second turning part, the first pipe upstream portion and the second pipe upstream portion can arrange along first pipe and the stacked direction of second pipe, and the first pipe downstream portion and the second pipe downstream portion can be along the stacked direction layouts of first pipe and second pipe.

Therefore, the temperature difference between second fluid that can reduce to flow through the first fluid of first pipe and flow through second pipe is poor with the thermal strain that alleviates between first pipe and second pipe.

According to an eighth aspect of the invention, the first pipe upstream portion and the second pipe upstream portion can be positioned at upstream side along the flow direction of the 3rd fluid with respect to the first pipe downstream portion and the second pipe downstream portion.

First fluid in being introduced in first heat exchange department and when being introduced in second fluid in second heat exchange department and having the temperature of the temperature that is higher than the 3rd fluid, can guarantee the temperature difference between first fluid and the 3rd fluid and the temperature difference between second fluid and the 3rd fluid at the upstream side of the fluid stream of the upstream side of the fluid of first pipe stream and second pipe, thus the amount of increase heat dissipation.Therefore, the thermal strain that can reduce between first pipe and second pipe is poor, thus the destruction of suppressing heat exchanger.

According to a ninth aspect of the invention, first pipe can comprise the upstream side first pipe group and the downstream first pipe group, the first fluid that wherein is introduced in first heat exchange department flows in the described upstream side first pipe group, the first fluid that flows from the upstream side first pipe group flows so that first fluid flows out first heat exchange department the first pipe group of described downstream, second pipe can comprise the upstream side second pipe group and the downstream second pipe group, second fluid that wherein is introduced in second heat exchange department flows in the described upstream side second pipe group, and second fluid that flows from the upstream side second pipe group flows so that second fluid flows out second heat exchange department the second pipe group of described downstream.In this case, first of the upstream side first pipe group and the upstream side second pipe group pipe upstream portion and the second pipe upstream portion can be positioned at upstream side along the flow direction of the 3rd fluid with respect to the first pipe downstream portion and the second pipe downstream portion.

First fluid in being introduced in first heat exchange department and when being introduced in second fluid in second heat exchange department and having the temperature of the temperature that is higher than the 3rd fluid, the temperature difference between first fluid and second fluid is reduced, and the while guarantees between first fluid and the 3rd fluid and the temperature difference between second fluid and the 3rd fluid at the upstream side of the fluid stream of the upstream side first and second pipe groups.Therefore, can increase the amount of heat dissipation.Therefore, thus can reduce first the pipe with second pipe between the thermal strain difference with the inhibition heat exchanger destruction.

According to the tenth aspect of the invention, first of the downstream first pipe group and the downstream second pipe group pipe upstream portion and the second pipe upstream portion can be positioned at the downstream along the flow direction of the 3rd fluid with respect to the first pipe downstream portion and the second pipe downstream portion.

First fluid in being introduced in first heat exchange department and when being introduced in second fluid in second heat exchanger and having the temperature of the temperature that is higher than the 3rd fluid, the heat that contains in the downstream first fluid of the fluid stream of downstream first and the second pipe group and second fluid can fully be dissipated in the 3rd fluid.Therefore, can improve the performance of heat exchanger.

According to an eleventh aspect of the invention, outer fin can be incorporated into first pipe and second pipe, and can be provided with for a plurality of slits that weaken the rigidity of outer fin partly.

Therefore, when the thermal strain difference between generation first pipe and second pipe, the slit of outer fin can the stress of absorption on each pipe.Further, even exist thermal strain poor between each pipe, be arranged on the slit in the outer fin also can suppress heat exchanger in the part scope destruction.

According to a twelfth aspect of the invention, the area of the coolant channel of the pars intermedia of at least one in first turning part and second turning part can be greater than the fluid inflow portion of a described turning part and each the area of fluid passage in the fluid outflow portion.

Therefore, when first fluid passes through first turning part, perhaps when second fluid passes through second turning part, can reduce the pressure loss.

According to a thirteenth aspect of the invention, interior fin can be arranged in first pipe and second pipe at least one heat exchange with promotion first fluid or second fluid and the 3rd fluid.In this case, interior fin can have the end in the inner space that is projected into first turning part or second turning part.

Therefore, the end of fin is projected in the inner space of first turning part or second turning part in each, thus in preventing fin manage with first and the interior perimeter surface of second pipe between be connected inefficacy.

According to a fourteenth aspect of the invention, each in first pipe and second pipe can be by making by the plate pipe that forms in conjunction with a pair of plate.Alternatively, each in first pipe and second pipe can form at the flat tube that the direction perpendicular to the longitudinal direction of pipe has flat cross section by bending.

Description of drawings

Reaching other purpose, structure and advantage more than of the present invention will be from becoming clear below in conjunction with the accompanying drawing detailed description of the invention, and described accompanying drawing has shown respectively:

Fig. 1 is the configured in one piece figure that shows according to first embodiment refrigerant flowpath of heat pump cycle in heating operation;

Fig. 2 is the configured in one piece figure that shows according to first embodiment refrigerant flowpath of heat pump cycle in defrost operation;

Fig. 3 is the configured in one piece figure that is presented among first embodiment refrigerant flowpath of heat pump cycle in the Waste Heat Recovery operation;

Fig. 4 is presented among first embodiment configured in one piece figure of the refrigerant flowpath of heat pump cycle in cooling down operation;

Fig. 5 is the perspective view of the profile of the heat exchanger among first embodiment;

Fig. 6 (a) is the front view of the pipe (pipe that is used for cooling medium) that is used for cold-producing medium in first embodiment; And Fig. 6 (b) is the side view that is used for the pipe of cold-producing medium among Fig. 6 (a);

Fig. 7 is the cutaway view that the line VII-VII along Fig. 6 (a) intercepts;

Fig. 8 is the cutaway view that the line VIII-VIII along Fig. 6 (a) intercepts;

Fig. 9 is the cutaway view that the line IX-IX along Fig. 6 (a) intercepts;

Figure 10 is in the cold-producing medium of the heat exchanger of first embodiment and the perspective schematic view of flow of coolant for explanation;

Figure 11 is the schematic part decomposition diagram of the heat exchanger among first embodiment;

Figure 12 is the perspective view according to the profile of the heat exchanger of second embodiment;

Figure 13 is for the cold-producing medium of the heat exchanger of explanation second embodiment and the perspective schematic view of flow of coolant;

Figure 14 is the schematic part decomposition diagram of the heat exchanger among second embodiment;

Figure 15 (a) is for the front view according to the pipe (pipe that is used for cooling medium) of the cold-producing medium of the heat exchanger of the 3rd embodiment; And Figure 15 (b) is the side view of the pipe that is used for cold-producing medium shown in Figure 15 (a);

Figure 16 is the configured in one piece figure of the refrigerant flowpath of heat pump cycle in the Waste Heat Recovery operation that shows according to the 4th embodiment;

Figure 17 is the perspective view according to the profile of the heat exchanger of the 5th embodiment;

Figure 18 is for the cold-producing medium of the heat exchanger of explanation the 5th embodiment and the schematic appearance perspective view of flow of coolant;

Figure 19 (a), 19 (b), 19 (c) and 19 (d) are according to the heat exchanger of other embodiment schematic cross sectional views along the longitudinal direction of header tank;

Figure 20 is the explanatory that causes the influence of temperature difference between the cold-producing medium of each pipe and the cooling agent for explanation owing to the architectural difference between each heat exchanger;

Figure 21 is the schematic part perspective view according to the heat exchanger of another embodiment; And

Figure 22 (a), 22 (b) and 22 (c) are for the explanatory of explanation according to the outside heat sink of another embodiment.

The specific embodiment

Below based on accompanying drawing embodiments of the invention are described.Parts identical or that be equal to are represented by identical Reference numeral in the drawings in following examples.

First embodiment

With reference to Fig. 1-11, the first embodiment of the present invention is described below.In this embodiment, heat exchanger 16 of the present invention is applied to for regulating the heat pump cycle 10 of the temperature that will be blown into the air in the vehicle interior at automotive air conditioner 1.Fig. 1-the 4th, the configured in one piece figure of the automotive air conditioner 1 in the present embodiment.Automotive air conditioner 1 is applied to so-called motor vehicle driven by mixed power, and described motor vehicle driven by mixed power can and be advanced from internal combustion engine (engine) and be obtained for the driving force of advancing with motor MG.

Motor vehicle driven by mixed power therein vehicle according to the load of advancing on the vehicle etc. by operation or stop engine from engine and advance with motor MG obtain travel condition that driving force advances and wherein vehicle only stop to switch between another travel condition of advancing with motor MG acquisition driving force from advancing by making engine.Therefore, compare with the common vehicle that only to be used for the driving force of advancing from engine, motor vehicle driven by mixed power can improve fuel efficiency.Heat pump cycle 10 in the automotive air conditioner 1 is vapor compression refrigeration cycles, and described vapor compression refrigeration cycles is used for heating or coolant compartment will be blown into conduct for the air of the vehicle interior in the space interested of air conditioning.That is, heat pump cycle 10 can switch between refrigerant flowpath, thereby carries out heating operation (heater operation) and cooling down operation (cooler operation).Carry out heating operation to heat vehicle interior by the air as the fluid interested that is used for heat exchange in the vehicle cabin.Carry out cooling down operation to cool off vehicle interior by the air in the coolant compartment.Then, heat pump cycle 10 can also be carried out defrost operation and Waste Heat Recovery operation.Carry out defrost operation and melt and remove the frost at outdoor heat exchange department 60 places that are formed on heat exchanger 16 in heating operation with the flow of the cold-producing medium, cooling agent or the extraneous air that flow through heat exchanger 16 by change, this will describe subsequently.Carry out the Waste Heat Recovery operation with will advance with the heat absorption of motor MG in the cold-producing medium with in heating operation as the external heat source.In the configured in one piece figure of the heat pump cycle 10 shown in Fig. 1-4, flowing of the cold-producing medium in the corresponding operating represented by filled arrows.

The heat pump cycle 10 of present embodiment adopts common fluorine-based cold-producing medium as cold-producing medium, and forms subcritical refrigeration cycle, and the high-pressure side refrigerant pressure of described subcritical refrigeration cycle is no more than the critical pressure of cold-producing medium.The refrigerating machine oil that is used for lubricate compressors 11 is mixed into cold-producing medium, and the part of refrigerating machine oil cycles through described circulation with cold-producing medium.

At first, compressor 11 is arranged in engine room, and sucks, compresses the cold-producing medium in the heat release pump circulation 10 side by side.Compressor is by utilizing motor 11b to drive the motor compressor of the fixed volume formula compressor 11a with fixed discharge capacity.Particularly, can adopt various types of compressing mechanisms such as volute type compressing mechanism or blade compresses mechanism as fixed volume formula compressor 11a.

Motor 11b is that its operation (revolution) is by the motor of controlling from the control signal of described air conditioning controller output subsequently.Motor 11b can use AC motor or DC motor.The cold-producing medium discharge capacity of the control break compressor 11 of the revolution of motor.Therefore, in the present embodiment, motor 11b is as the discharge capacity modifier of compressor 11.

The cold-producing medium discharge port of compressor 11 is connected to the refrigerant inlet side as the indoor condenser 12 of user's side heat exchanger.Indoor condenser 12 is arranged on the housing 31 for the room air regulon 30 of the air regulator 1 of vehicle.Indoor condenser be for the high-temperature high-pressure refrigerant that flows through it and compartment by the air of described indoor evaporator 20 subsequently between the heating heat exchanger of heat-shift.The detailed construction of room air regulon 30 will be described subsequently.

Heating is connected to the refrigerant outlet side of indoor condenser 12 with fixed restriction device 13.Fixed restriction device 13 usefulness act on the decompressor of heating operation, the cold-producing medium that described decompressor reduces pressure in heating operation and expands and flow out from indoor condenser 12.Heating can be used aperture, capillary etc. with fixed restriction device 13.Heating is connected to the refrigerant inlet side of the outdoor heat exchange department 60 of composite heat exchanger 16 with the outlet side of fixed restriction device 13.

The bypass passageways 14 that is used for described fixed restriction device is connected to the refrigerant outlet side of indoor condenser 12.Bypass passageways 14 makes refrigerant bypass (walking around) heating of flowing out from indoor condenser 12 with fixed restriction device 13 and cold-producing medium is directed to the outdoor heat exchange department 60 of heat exchanger 16.The open/closed valve 15a that be used for to open and close is used for the bypass passageways 14 of fixed restriction device is arranged on the bypass passageways 14 for the fixed restriction device.Open/closed valve 15a is magnetic valve, and the opening and closing operation of described magnetic valve is by the control Control of Voltage from the output of air conditioning controller.

Compare with the pressure loss that produces during by fixed restriction device 13 when cold-producing medium, the pressure loss that produces during by open/closed valve 15a when cold-producing medium is extremely little.Therefore, when open/closed valve 15a opened, the cold-producing medium that flows out from indoor condenser 12 flow into the outdoor heat exchange department 60 of heat exchanger 16 via the bypass passageways 14 that is used for the fixed restriction device.On the contrary, when open/closed valve 15a closed, cold-producing medium flow in the outdoor heat exchange department 60 of heat exchanger 16 with fixed restriction device 13 via heating.

Therefore, open/closed valve 15a can switch between the refrigerant flowpath of heat pump cycle 10.The open/closed valve 15a of present embodiment is as the refrigerant flowpath switching device shifter.Alternatively, as this refrigerant flowpath switching device shifter, electric T-shaped valve etc. can be set to be connected to heating and to switch with between the refrigerant loop of the entrance side of fixed restriction device 13 and another refrigerant loop that is connected to for the outlet side with indoor condenser 12 for the entrance side of the bypass passageways 14 of fixed restriction device being used for outlet side with indoor condenser 12.

Heat exchanger 16 is arranged in the engine room.The outdoor heat exchange department 60 of heat exchanger 16 is the heat exchange departments for heat-shift between the low pressure refrigerant that flows through described outdoor heat exchange department 60 and the extraneous air that blows from blower fan 17.In addition, outdoor heat exchange department 60 as evaporation low pressure refrigerant in heating operation showing the evaporation heat exchange department of heat absorption effect, and as dissipation in cooling down operation from the heat transmission heat exchange department of the heat of high-pressure refrigerant.

Blower fan 17 is operating ratios, i.e. revolution (air capacity) is by the voltage-controlled electric blower of control from the output of air conditioning controller.The heat exchanger 16 of present embodiment forms one with radiator 70, wherein said radiator 70 be used for the extraneous air that blows from blower fan 17 with cycle through above outdoor heat exchange department 60 and be used for the cooling heat-shift between the cooling agent of the coolant circulation circuit 40 of using motor MG of advancing.

Blower fan 17 usefulness of present embodiment act on the extraneous air outdoor blowing device that both blow towards the outdoor heat exchange department 60 of heat exchanger 16 and radiator 70.Below describe the detailed construction of the composite heat exchanger 16 that comprises coolant circulation circuit integrally formed with each other 40, outdoor heat exchange department 60 and radiator 70 in detail.

The outlet side of the outdoor heat exchange department 60 of heat exchanger 16 is connected to electric T-shaped valve 15b.The operation of triple valve 15b is by the control Control of Voltage from the output of air conditioning controller.Triple valve 15b is used as the refrigerant flowpath switching device shifter with above open/closed valve 15a.

More specifically, in heating operation, triple valve 15b carries out to switch to for the outlet side with outdoor heat converter 19 and is connected to the switching of the refrigerant flowpath of the entrance side of described holder 18 subsequently.On the contrary, in cooling down operation, triple valve 15b carries out to switch to for the outlet side with the outdoor heat exchange department 60 of heat exchanger 16 and is connected to cooling with the switching of the refrigerant flowpath of the entrance side of fixed restriction device 19.Cooling acts on the decompressor of cooling down operation with fixed restriction device 19 usefulness, and described decompressor is used for the cold-producing medium that flows out from outdoor heat exchange department 60 is reduced pressure and expanding at cooling down operation.Fixed restriction device 19 has identical basic structure with above heating with fixed restriction device 13.

Cooling is connected to the refrigerant inlet side of indoor evaporator 20 with the outlet side of fixed restriction device 19.Indoor evaporator 20 is arranged on the upstream side of air-flow with respect to indoor condenser 12 in the housing 31 of room air regulon 30.Indoor evaporator 20 is that heat exchanger use in cooling, thus described cooling with heat exchanger in the compartment air and flow through between the cold-producing medium of described heat exchanger heat-shift to cool off the air in the vehicle interior.

The refrigerant outlet side of indoor evaporator 20 is connected to the entrance side of holder 18.Holder 18 is that the cold-producing medium that will flow in the holder 18 is separated into the gas-liquid separator that is used for the low-pressure side cold-producing medium of liquid and gas, and stores the excess refrigerant in the circulation in it.The vapor phase refrigerant outlet of holder 18 is connected to the suction side of compressor 11.Therefore, compressed in compressor 11 to prevent liquid thereby holder 18 is sucked into compressor 11 for the inhibition liquid phase refrigerant.

Next, room air regulon 30 is below described.Room air regulon 30 is arranged on instrument board (instrument panel) inside at the forefront place in compartment.Room air regulon 30 holds air blast 32, above-mentioned indoor condenser 12 and indoor evaporator 20 in the housing 31 that forms shell.

Housing 31 is formed for making the air flow air passage in the compartment that is blown in the vehicle interior.Housing 31 by have to a certain degree elasticity and the resin (for example, polypropylene) of fabulous intensity form.The inner/outer air switch 33 that is used for switching between the air (inner air) of vehicle interior and extraneous air is arranged on the upstream side of vehicle interior air stream in housing 31.

Inner/outer air switch 33 is provided with for the inner air entrance that inner air is incorporated into housing 31 with for the extraneous air entrance that extraneous air is incorporated into housing 31.The inner/outer air switches door and is positioned at inner/outer air switch 33 inside with the aperture area of continuous adjusting inner air entrance and extraneous air entrance, thereby changes the volume ratio of inner air and extraneous air.

Be used for to be arranged on the downstream of the air stream of inner/outer air switch 33 via the air blast 32 that inner/outer air switch 33 inhaled airs are blown into vehicle interior.Air blast 32 is electric blowers, and described electric blower comprises by electric motor driven centrifugal multi-blade fan (Sirocco fan), and the revolution of described electric blower (air capacity) is by the control Control of Voltage from the output of air conditioning controller.

Indoor evaporator 20 and indoor condenser 12 are arranged on the downstream of the air stream of air blast 32 in this order with respect to the stream of the air in the vehicle interior.In brief, indoor evaporator 20 is arranged on upstream side with respect to indoor condenser 12 along the flow direction of the air in the compartment.

Air mix door 34 is arranged on the downstream of the air stream in the indoor evaporator 20 and at the upstream side of the air stream of indoor condenser 12.Air mix door 34 is by regulating the volume flow by the air of indoor condenser 12 in the air of indoor evaporator 20.Blending space 35 is arranged on the downstream of the air stream in the indoor condenser 12 so that cross indoor condenser 12 and do not have heated air to mix with bypass with cold-producing medium heat-shift and heated air at indoor condenser 12 places.

Be used for and be blown into the downstream that in housing 31, is arranged on air stream as the air outlet slit in the vehicle interior in the space interested that will be cooled at blending space 35 mixed adjusting air.Particularly, the air outlet slit (not shown) comprises for regulating facial air outlet slit that the upper body of air towards the passenger in compartment blow, be used for regulating foot's air outlet slit that air blows towards passenger's foot and be used for regulating the defrost air that air blows towards the inboard of the windshield of vehicle and exporting.

Air mix door 34 is regulated the volume flow by the air of indoor condenser 12, thereby is adjusted in the temperature of adjusting air mixed in the blending space 35, thereby controls the temperature of the adjusting air that blows from each air outlet slit.That is, air mix door 34 usefulness act on the temperature-adjusting device of regulating the temperature that is blown into the adjusting air in the vehicle interior.

In brief, air mix door 34 usefulness act on be adjusted in as in the indoor condenser 12 of user's side heat exchanger at the air of vehicle interior and from the heat exchange amount adjusting device of the amount of the heat that exchanges between the cold-producing medium of compressor 11 dischargings.Air mix door 34 is driven by the servo motor (not shown), and the operation of described servo motor is based on being controlled from the control signal of air conditioning controller output.

Foot's door and being used for that the respective upstream side that facial air outlet slit, foot's air outlet slit and defrost air outlet are flowed at its air has facial door for the aperture area of regulating facial air outlet slit respectively, be used for regulating the aperture area of foot's air outlet slit is regulated the defrosting door (all doors are all not shown) of the aperture area of defrost air outlet.

Facial door, foot's door and defrosting door are with act on the air outlet slit mode-changeover device that switches between the air outlet slit pattern.Each door is driven by the servo motor (not shown), the operation of described servo motor via linkage etc. based on being controlled from the control signal of air conditioning controller output.Next, below coolant circulation circuit 40 will be described.Coolant circulation circuit 40 is (for example to allow cooling agent for passing through, glycol water) cycle through as cooling medium (heat medium) and be formed on above advancing and cool off the cooling medium closed circuit of advancing with motor MG with the coolant channel among the motor MG, described advancing with motor MG is one of car-mounted device that produces in operation heat.

Coolant circulation circuit 40 is provided with the radiator 70 of cooling medium pump 41, electric T-shaped valve 42, composite heat exchanger 16 and is used for allowing cooling agent to walk around the bypass passageways 44 that radiator 70 flows.

Cooling medium pump 41 is being formed on the electrodynamic pump of advancing with in the coolant channel in the motor MG at coolant circulation circuit 40 cooling agent being expressed to, and the revolution of described electrodynamic pump (flow) is by the control signal control from the output of air conditioning controller.Therefore, cooling medium pump 41 usefulness act on by change being used for cooling and advance and regulate the cooling capacity adjusting device of cooling capacity with the flow of the cooling agent of motor MG.

Triple valve 42 makes cooling agent flow into the cooling medium loop of radiator 70 at the outlet side that is used for being connected to by the entrance side with cooling medium pump 41 radiator 70 to switch with making between ANALYSIS OF COOLANT FLOW another cooling medium loop with bypass radiator 70 for the outlet side that is connected to bypass passageways 44 by the entrance side with cooling medium pump 41.Operation acts on the loop switching device shifter that switches by voltage-controlled triple valve 42 usefulness of control from the output of air conditioning controller between the cooling medium loop.

That is, the coolant circulation circuit 40 of present embodiment can make cooling agent cooling agent in order from cooling medium pump 41 to advance another the cooling medium loop of with motor MG, radiator 70 and cooling medium pump 41 circulating be switched to advancing with cooling medium loop of motor MG, bypass passageways 44 and cooling medium pump 41 circulations and being used for shown in the dotted arrow of Fig. 2 etc. from cooling medium pump 41 in order in being used for shown in the dotted arrow of Fig. 1 etc.

Therefore, when the operating period of the electricity consumption motivation MG that advances triple valve 42 carry out to when being used for allowing cooling agent from the switching of bypass by the cooling medium loop of radiator 70, cooling agent is the temperature rising under situation about its heat not being dissipated in the radiator 70.That is, when triple valve 42 was carried out to the switching in the cooling medium loop that is used for allowing cooling agent to pass through radiator 70 from bypass, advancing was stored in the cooling agent with the heat that contains among the motor MG (heat of generation).

On the contrary, when triple valve 42 was carried out to the switching in the cooling medium loop that is used for allowing cooling agent to pass through radiator 70 in the operating period of the electricity consumption motivation MG that advances, cooling agent flow in the radiator 70 then and the extraneous air heat-shift that blows from blower fan 17.The heat exchanger 16 of present embodiment allow to flow in the radiator 70 cooling agent not only with extraneous air and also with the cold-producing medium heat-shift that flows through outdoor heat exchange department 60.Next, will use Fig. 5-11 to describe the composite heat exchanger 16 of present embodiment in detail.Fig. 5 shows the perspective view of profile of the heat exchanger 16 of present embodiment.Fig. 6 (a) is presented at the front view of the pipe 61 (pipe 71 of cooling medium) of the cold-producing medium that is used for outdoor heat exchange department 60 (radiator 70) among first embodiment.Fig. 6 (b) shows the side view of the pipe of Fig. 6 (a).Fig. 7 shows the amplification view that intercepts along the line VII-VII of Fig. 6 (a).Fig. 8 shows the cutaway view that intercepts along the line VIII-VIII of Fig. 6 (a).Fig. 9 shows the amplification view that intercepts along the line IX-IX of Fig. 6 (a).Figure 10 shows for the cold-producing medium of explanation heat exchanger 16 and the perspective schematic view of flow of coolant.As shown in Figure 5, the outdoor heat exchange department 60 of heat exchanger 16 and radiator 70 comprise be used to a plurality of pipes that cold-producing medium or ANALYSIS OF COOLANT FLOW are passed through (61 and 71) and are used for collection and the header tank (62 and 72) of distribution, described header tank is arranged on each along the longitudinal direction distolateral in the pipe and goes up and be suitable for collecting and distributing cold-producing medium or the cooling agent that flows through pipe, thereby forms usually said header tank and tubing heat exchanger structure.

Particularly, outdoor heat exchange department 60 comprises for a plurality of refrigerant pipes 61 that allow to pass through as the flow of refrigerant of first fluid and the refrigerant side header tank 62 that extends to collect or distribute the cold-producing medium that flows through refrigerant pipe 61 along the stacked direction of pipe 61.Outdoor heat exchange department 60 is at the heat exchange department that flows through heat-shift between pipe 61 cold-producing medium and the air (extraneous air that blows from blower fan 17) that flows through refrigerant pipe 61 conduct the 3rd fluid on every side.On the contrary, radiator 70 comprises for a plurality of cooling medium pipes 71 that allow to pass through as the ANALYSIS OF COOLANT FLOW of second fluid and the cooling medium side header tank 72 that extends to collect or distribute the cooling agent that flows through pipe 71 along the stacked direction of pipe 71.Radiator 70 be for flow through pipe 71 cooling agent with at pipe 71 heat exchange department of heat-shift between the flow air (extraneous air that blows from blower fan 17) on every side.In the present embodiment, shown in 6 (a) and 6 (b), in refrigerant pipe 61 and the cooling medium pipe 71 each all adopts usually said plate pipe, described plate pipe has recess and lug boss so that the centrally aligned of the center of a plate and another plate by in conjunction with forming among a pair of plate 61a and the 61b (71a and 71b) on the surface of each plate.Plate 61a and 61b (71a and 71b) are formed by the metal with fabulous thermal conductivity (being aluminium alloy in the present embodiment).Refrigerant pipe 61 in the present embodiment has identical basic structure with cooling medium pipe 71.Fig. 6 (a) and 6 (b) have shown refrigerant pipe 61, and simultaneously the parts corresponding to the parts of refrigerant pipe 61 of cooling medium pipe 71 are represented by the respective drawings mark in the bracket.As shown in Figure 5, described refrigerant side header tank 62 extends with the direction of cooling medium side header tank 72 refrigerant pipe 61 being connected subsequently with cooling medium pipe 71, and is arranged between refrigerant side header tank 62 and the cooling medium side header tank 72.In brief, refrigerant side header tank 62 be positioned at each along the longitudinal direction one in refrigerant pipe 61 and the cooling medium pipe 71 distolateral on.Cooling medium side header tank 72 be positioned at each along the longitudinal direction another in refrigerant pipe 61 and the cooling medium pipe 71 distolateral on.In refrigerant pipe 61 and the cooling medium pipe 71 each all has the end that is fixed to refrigerant side header tank 62 and another end that is fixed to cooling medium side header tank 72 in a longitudinal direction in a longitudinal direction.Shown in Fig. 6 (a) and 6 (b), refrigerant pipe 61 extends at the longitudinal direction of refrigerant pipe 61 (perpendicular to the direction of the flow direction of the extraneous air that blows from blower fan 17).Shown in the cutaway view of Fig. 7, the refrigerant flowpath 61c with flat cross section is arranged to two row along the flow direction of the extraneous air that blows from blower fan 17.Therefore, the outer surface of part that forms the refrigerant flowpath 61c of refrigerant pipe 61 is the flat surfaces 61d that is parallel to the flow direction expansion of the extraneous air that blows from blower fan 17.Shown in the cutaway view of Fig. 8, be arranged among two refrigerant flowpath 61c of two row each in the end of refrigerant side header tank 62 sides at the place, end of refrigerant pipe 61 towards outside opening.In the present embodiment, refrigerant side header tank 62 is placed on the open end of refrigerant flowpath 61c, makes two refrigerant flowpath 61c all be communicated with the inner space of refrigerant side header tank 62.On the contrary, shown in the cutaway view of Fig. 9, be arranged among two refrigerant flowpath 61c of two row each in another ends of cooling medium side header tank 72 sides not towards the outside outwards opening of refrigerant pipe 61, and two row refrigerant flowpath 61c link together by refrigerant side turning part 61e.Like this, the inner space of cooling medium side header tank 72 is not communicated with refrigerant pipe 61, makes two row refrigerant flowpath 61c communicate with each other.

Therefore, in the refrigerant pipe 61 of present embodiment, refrigerant side turning part 61e is oriented to compare more near cooling medium side header tank 72 with refrigerant side header tank 62.As by shown in the filled arrows of Figure 10, the flow direction that flow into one cold-producing medium among the refrigerant flowpath 61c that is arranged to two row from refrigerant side header tank 62 is reverse at refrigerant side turning part 61e, and flow among another refrigerant flowpath 61c to turn back to refrigerant side header tank 62.The area of the coolant channel of refrigerant side turning part 61e is greater than the area of the coolant channel of refrigerant flowpath 61c.That is, the area of the coolant channel of the pars intermedia of refrigerant side turning part 61e is greater than the cold-producing medium inflow portion that is connected to refrigerant flowpath 61c of refrigerant side turning part 61e and each the area in the cold-producing medium outflow portion.The coolant channel area is defined as the area of section perpendicular to the flow direction of cold-producing medium.Another end place relative with refrigerant side turning point 61e at the refrigerant flowpath 61c of refrigerant pipe 61 arranges expansion section 61f to enlarge the coolant channel area of refrigerant flowpath 61c.Two refrigerant flowpath 61c are communicated with the inner space of refrigerant side header tank 62 via expansion section 61f.Expansion section 61f is formed the surface area of the inboard that enlarges refrigerant pipe 61 to improve pressure drag.The interior fin 65 of the heat exchange between the extraneous air that be used for to promote cold-producing medium and blow from blower fan 17 is arranged in the refrigerant flowpath 61c of refrigerant pipe 61.Interior fin 65 forms by metal sheet is bent to waveform shape.As Fig. 8 and shown in Figure 9, interior fin 65 has two ends in the inner space that is projected into expansion section 61f and refrigerant side turning part 61e respectively in a longitudinal direction.In cooling medium pipe 71, be similar to refrigerant pipe 61, the cooling medium flow path 71c with flat cross section is arranged to two row along the flow direction of the extraneous air that blows from blower fan 17.Therefore, the outer surface of part that forms the cooling medium flow path 71c of cooling medium pipe 71 is the flat surfaces 71d that is parallel to the flow direction expansion of the extraneous air that blows from blower fan 17.Each cooling medium flow path 71c of cooling medium pipe 71 has an end that is communicated with in the inner space with cooling medium side header tank 72 of cooling medium side header tank 72 sides.Another end in cold-producing medium header tank 62 sides of two cooling medium flow path 71c is connected to the cooling medium side turning part 71e with structure identical with the structure of refrigerant side turning part 61e.Therefore, in cooling medium pipe 71, cooling medium side turning part 71e is oriented to compare more near refrigerant side header tank 62 with cooling medium side header tank 72.As by shown in the dotted arrow of Figure 10, the flow direction that flow into the cold-producing medium in that is arranged among the two cooling medium flow path 71c that go from cooling medium side header tank 72 is reverse at cooling medium side turning part 71e, and flow among another refrigerant flowpath 71c to turn back to cooling medium side header tank 72.The interior fin 75 of the heat exchange between the extraneous air that be used for to promote cooling agent and blow from blower fan 17 is arranged in the cooling medium flow path 71c of cooling medium pipe 71.Interior fin 75 have be arranged on refrigerant flowpath 61c in the identical structure of the structure of interior fin 65.Interior fin 75 has two ends in the inner space that is projected into expansion section 71f and cooling medium side turning part 71e respectively in a longitudinal direction.In refrigerant pipe 61 and cooling medium pipe 71, flat surfaces 61d and the 71d of the outer surface of pipe are parallel stacked with the preset distance between it.That is, refrigerant pipe 61 is arranged between the cooling medium pipe 71.On the contrary, cooling medium pipe 71 is arranged between the refrigerant pipe 61.The space that is formed between refrigerant pipe 61 and the cooling medium pipe 71 is formed for allowing the outside absolutely empty air-flow from blower fan 17 blows to move the outside air opening 16a (the 3rd fluid passage) that passes through.Externally among the air duct 16a, outer fin 50 is configured to be connected with the flat surfaces 61d of refrigerant pipe 61 respect to one another and the flat surfaces 71d of cooling medium pipe 71.Outer fin 50 can promote heat exchange between the cold-producing medium in extraneous air and the outdoor heat exchange department 60 and the heat exchange between the cooling agent in extraneous air and the radiator 70.Further, outer fin 50 can and flow through at the cold-producing medium that flows through refrigerant pipe 61 and carry out heat transmission between the cooling agent of cooling medium pipe 71.The outer fin 50 that uses is by metal sheet being bent to the corrugated fin that waveform shape forms.In the present embodiment, outer fin 50 be connected to refrigerant pipe 61 and cooling medium pipe 71 both, thereby make it possible between refrigerant pipe 61 and cooling medium pipe 71, carry out heat transmission.

The detailed construction of refrigerant pipe 61, cooling medium pipe 71, refrigerant side header tank 62 and cooling medium side header tank 72 is described with reference to Figure 11 next.Figure 11 has shown the schematic part decomposition diagram of heat exchanger 16.For easy understanding, Figure 11 has omitted the diagram of outer fin 50.As shown in figure 11, each refrigerant pipe 61 all comprises the refrigerant pipe upstream portion 611 and the refrigerant pipe downstream portion 612 that is positioned at the downstream of refrigerant side turning part 61e of the upstream side that is positioned at refrigerant side turning part 61e.That is, the refrigerant pipe 61 of present embodiment is made up of refrigerant pipe upstream portion 611, refrigerant side turning part 61e and refrigerant pipe downstream portion 612.In the refrigerant pipe 61 of present embodiment, refrigerant pipe upstream portion 611 is arranged on the downstream with respect to refrigerant pipe downstream portion 612 along the flow direction A of extraneous air.On the contrary, each cooling medium pipe 71 all comprises the cooling medium pipe upstream portion 711 and the cooling medium pipe downstream portion 712 that is positioned at the downstream of cooling medium side turning part 71e of the upstream side that is positioned at cooling medium side turning part 71e.That is, the cooling medium pipe 71 of present embodiment is made up of cooling medium pipe upstream portion 711, cooling medium side turning part 71e and cooling medium pipe downstream portion 712.In the cooling medium pipe 71 of present embodiment, cooling medium pipe upstream portion 711 is arranged on upstream side with respect to cooling medium pipe downstream portion 712 along the flow direction A of extraneous air.Refrigerant pipe 61 in the present embodiment and cooling medium pipe 71 are configured such that the stacked direction of refrigerant pipe upstream portion 611 and cooling medium pipe downstream portion 712 edge pipes 61 and 71 is arranged and the stacked direction layout of refrigerant pipe downstream portion 612 and cooling medium pipe upstream portion 711 edge pipes 61 and 71.By this structure, the cold-producing medium that flows through refrigerant pipe 61 flow to upstream side from the downstream along the flow direction of extraneous air, and the cooling agent that flows through cooling medium pipe 71 flow to the downstream from the upstream side along the flow direction of extraneous air.Therefore, in refrigerant pipe 61 and cooling medium pipe 71, with respect to the flow direction A of extraneous air, the flow direction of cold-producing medium that flows through refrigerant pipe 61 is opposite with the flow of coolant direction that flows through cooling medium pipe 71.

Next, refrigerant side header tank 62 and cooling medium side header tank 72 below will be described.Refrigerant side header tank 62 has the basic structure identical with the basic structure of cooling medium side header tank 72.Refrigerant side header tank 62 comprises both cold-producing medium side plates 63 of fixedly refrigerant pipe 61 and cooling medium pipe 71 and is fixed to the refrigerant side case 64 of cold-producing medium side plate 63.

The part corresponding to each refrigerant pipe 61 of cold-producing medium side plate 63 is provided with the intercommunicating pore that runs through plate.Refrigerant pipe 61 passes intercommunicating pore.Therefore, the refrigerant flowpath 61c of each refrigerant pipe 61 is communicated with the inner space of refrigerant side header tank 62.Part in the insertion intercommunicating pore of refrigerant pipe 61 is shorter than the width of refrigerant flowpath 61c along the width of the flow direction of extraneous air.Similarly, the part corresponding to each cooling medium pipe 71 of cold-producing medium side plate 63 is provided with the intercommunicating pore that runs through plate.Cooling medium pipe 71 inserts in the intercommunicating pore, makes the hole be closed.Part in the insertion intercommunicating pore of cooling medium pipe 71 is shorter than the width of cooling medium flow path 71c along the width of the flow direction of extraneous air.Thereby cold-producing medium side plate 63 is fixed to refrigerant side case 64 to be formed for being separated to form the recess 63a in the space between plate 63 and case 64.Recess 63a is arranged on the whole zone of cold-producing medium side plate 63 in a longitudinal direction.Thereby refrigerant side case 64 is fixed to cold-producing medium side plate 63 to be formed for that cold-producing medium collected collection space 62a within it and to be used for the allocation space 62b of assignment system cryogen.Particularly, refrigerant side case 64 forms by two mountains (W shape) shape that flat metal sheets is squeezed into when seeing in a longitudinal direction.The central part 64a of two chevron shapes of refrigerant side case 64 is connected to the recess 63a of cold-producing medium side plate 63, thereby the inner space is separated into collection space 62a and allocation space 62b.In the present embodiment, collection space 62a is arranged on weather side along the flow direction A of extraneous air, and allocation space 62b is arranged on downwind side along the flow direction A of extraneous air.As mentioned above, refrigerant pipe 61 passes the intercommunicating pore of cold-producing medium side plate 63, make the refrigerant flowpath 61c (refrigerant pipe downstream portion 612) that is arranged on weather side along the flow direction A of extraneous air be communicated with collection space 62a, and be communicated with allocation space 62b along the refrigerant flowpath 61c (refrigerant pipe upstream portion 611) that the flow direction A of extraneous air is arranged on downwind side.As shown in Figure 5, an end along the longitudinal direction of refrigerant side case 64 is connected to for the cold-producing medium inlet tube 64b that cold-producing medium is incorporated into allocation space 62b and is used for guiding from the cold-producing medium guide pipe 64c of the cold-producing medium of collection space 62a.Refrigerant side case 64 other end along the longitudinal direction is closed the member closure.

In addition, as shown in figure 11, cooling medium side header tank 72 also comprises cooling medium side plate 73 and cooling medium side case 74.Cooling medium pipe 71 passes the intercommunicating pore corresponding to the part place of cooling medium pipe 71 that is arranged on cooling medium plate 73.Refrigerant pipe 61 inserts in another intercommunicating pore corresponding to the part place of refrigerant pipe 61 that is arranged on cooling medium plate 73.Cooling medium side case 74 is fixed to cooling medium side plate 73, make the recess 73a of cooling medium side plate 73 be connected to the central part 74a of two chevron shapes of cooling medium side case 74, thereby the inner space is separated into for cold-producing medium being collected collection space 72a within it and being used for the allocation space 72b of assignment system cryogen.In the present embodiment, allocation space 72b is arranged on weather side along the flow direction A of extraneous air, and collection space 72a is arranged on downwind side along the flow direction A of extraneous air.As mentioned above, refrigerant pipe 71 passes the intercommunicating pore of cooling medium side plate 73, make the cooling medium flow path 71c (cooling medium pipe upstream portion 711) that is arranged on weather side along the flow direction A of extraneous air be communicated with allocation space 72b, and be communicated with collection space 72b along the cooling medium flow path 71c (cooling medium pipe downstream portion 712) that the flow direction A of extraneous air is arranged on downwind side.

As shown in Figure 5, cooling medium side case 74 is connected to for the cooling medium inlet tube 74b that cooling medium is incorporated into allocation space 72b with for the cooling medium guide pipe 74c from collection space 72a guiding and derivation cooling medium at an end of longitudinal direction.The other end along the longitudinal direction of cooling medium side header tank 72 is by the enclosed member closure.

Therefore, in the heat exchanger 16 of present embodiment, shown in the perspective schematic view of Figure 10, be introduced in cold-producing medium among the allocation space 62b of refrigerant side header tank 62 via cold-producing medium inlet tube 64b and flow in the two row refrigerant pipes 61 along the flow direction A of extraneous air and be arranged among each refrigerant flowpath 61c (refrigerant pipe upstream portion 611) of a refrigerant pipe of downwind side.

Then, the cold-producing medium that flows from the refrigerant flowpath 61c (refrigerant pipe upstream portion 611) that is arranged on downwind side flow into another refrigerant flowpath 61 ((refrigerant pipe downstream portion 612)) that is arranged on weather side via refrigerant side turning part 61e.Further, collect the collection space 62a of refrigerant side header tank 62 from the cold-producing medium that the refrigerant flowpath 61c (refrigerant pipe downstream portion 612) that is arranged on weather side flows, derive from cold-producing medium guide pipe 64c then.Namely, in the heat exchanger 16 of present embodiment, cold-producing medium flows and turns to refrigerant side turning part 61e with in refrigerant flowpath 61c (the refrigerant pipe downstream portion 612) order of the weather side of refrigerant pipe 61 successively from the refrigerant flowpath 61c of the downwind side (refrigerant pipe upstream portion 611) of refrigerant pipe 61.Equally, cooling medium flow path 71c (the cooling medium pipe downstream portion 712) order of cooling agent from the cooling medium flow path 71c (cooling medium pipe upstream portion 711) of the weather side of cooling medium pipe 71 to the downwind side of cooling medium side turning part 71e and cooling medium pipe 71 flows and turns to.Therefore, have the flow direction opposite with the flow of coolant direction that flows through adjacent cooling medium pipe 71 (this is called as " reverse flow structure ") along pipe 61 and 71 longitudinal direction with along the cold-producing medium that the flow direction of extraneous air flows through adjacent refrigerant pipe 61.More than in the parts of fin 65 and 72, refrigerant side header tank 62, cooling medium side header tank 72 and outer fin 50 formed by the metal identical with the metal of plate 61a, the 61b, 71a and the 71b that form refrigerant pipe 61 and cooling medium pipe 71.The manufacture method of heat exchanger 16 is below described.At first, refrigerant pipe 61, cooling medium pipe 71, refrigerant side header tank 62 and cooling medium side header tank 72 are temporarily fixed (this is called as " the temporary fixed step of pipe-case ").Particularly, in refrigerant pipe 61, plate 61a and 61b are assembled into and make the center of a plate and the centrally aligned of another plate, and interior fin 65 is assembled to refrigerant flowpath 61c.Claw be formed on plate 61 along in the upstream side of the flow direction of extraneous air and in the downstream at least one (whole zone in vertical direction in the present embodiment).Claw is towards plate 61b bending.In the present embodiment, plate 61a comprises the claw 61g that is formed between the refrigerant flowpath 61c that are arranged to two row, and described claw is bent in the through hole that is formed among the plate 61b, makes plate 61a be temporarily fixed plate 61b.Equally, in cooling medium pipe 71, plate 71a and 71b and interior fin 75 are temporarily fixed is in the same place.In refrigerant side header tank 62, cold-producing medium side plate 63 and refrigerant case 64 combine by the claw that is bent to form in refrigerant slabs 63 at the peripheral end place of refrigerant side case 64, make plate 63 and 64 be temporarily fixed.In addition, in cooling medium header tank 72, cooling medium side plate 73 and cooling medium case 74 are temporarily fixed.The order of temporary fixed refrigerant pipe 61, cooling medium pipe 71, refrigerant side header tank 62 and cooling medium side header tank 72 is not subject to said sequence.Then, refrigerant pipe 61 and cooling medium pipe 71 insert respectively in the cold-producing medium side plate 63 that is arranged on cold-producing medium header tank 62 and the cooling medium side plate 73 of cooling medium side header tank 72 in intercommunicating pore in.At this moment, in the present embodiment, pipe is inserted into and makes that the edge of opening of corresponding intercommunicating pore and the distance between among turning part 61e and 71e and expansion section 61f and the 71f each are 3mm or littler.Outer fin 50 inserts and temporarily anchors to the outside air opening 16a that is formed in refrigerant pipe 61 and the cooling medium pipe 71, and introducing/guide pipe 64b, 64c, 74b and 74c are temporarily fixed (this is called as " the temporary fixed step of heat exchanger ") accordingly then.After the fixing heat exchanger of temporarily being assembled by wire holder etc. 16, whole heat exchanger 16 is placed in the heating furnace and is heated.At this moment, the scolder that is coated to the surface of each parts in advance is melted, and heat exchanger 16 is cooled till scolder solidifies again.Therefore, each parts are by one welding (this is called as " heat exchanger integrating step ").Above method can produce the heat exchanger that comprises outdoor heat exchange department 60 integral with one another and radiator 70.As finding out from the above description, for example, the outdoor heat exchange department 60 of present embodiment is corresponding to first heat exchange department; Refrigerant pipe 61 is corresponding to first pipe; Refrigerant side header tank 62 is corresponding to first case; And refrigerant side turning part 61e is corresponding to first turning part.For example, the refrigerant pipe upstream portion 611 of refrigerant pipe 61 is corresponding to the first pipe upstream portion; And refrigerant pipe downstream portion 612 is corresponding to the first pipe downstream portion.On the contrary, for example, radiator 70 is corresponding to second heat exchange department; Cooling medium pipe 71 is corresponding to second pipe; Cooling medium side header tank 72 is corresponding to second case; And cooling medium side turning part 71e is corresponding to second turning part.For example, the cooling medium pipe upstream portion 711 of cooling medium pipe 71 is corresponding to the second pipe upstream portion; And cooling medium pipe downstream portion 712 is corresponding to the second pipe downstream portion.The electric control unit of present embodiment is below described.The air conditioning controller is made of the known microcomputer that comprises CPU, ROM and RAM and peripheral circuit thereof.Control module is by carrying out various operations and handle various types of air conditioning controllers 11 of the output that is operatively connected to above-mentioned control module, each operation among 15a, the 15b, 17,41 and 42 according to being stored in air conditioning control program among the ROM.The one group of various sensor that is used for the control air conditioning are connected to the input side of air conditioning controller.Sensor comprises inner air sensor for detection of the temperature of vehicle interior, for detection of the extraneous air sensor of the temperature of extraneous air, for detection of the solar radiation sensor of the amount of the solar radiation in the vehicle interior with for detection of the evaporator temperature sensor of the temperature (evaporator temperature) of the air that blows from indoor evaporator 20.In addition, sensor also comprises for detection of from the refrigerant emission temperature sensor of the temperature of the cold-producing medium of compressor 11 discharging, for detection of the outlet refrigerant temperature sensors 51 of the refrigerant temperature Te of the outlet side of outdoor heat exchange department 60 with as for detection of flowing into the coolant temperature sensor 52 of advancing with the coolant temperature checkout gear of the coolant temperature Tw of the cooling agent the motor MG.In the present embodiment, coolant temperature sensor 52 detects the coolant temperature Tw of the cooling agent that squeezes out from cooling medium pump 41.Alternatively, can detect the coolant temperature Tw of the cooling agent that is inhaled in the cooling medium pump 41.The guidance panel (not shown) of the instrument board setting of close front, compartment is connected to the input side of air conditioning controller.From being arranged on the various types of air conditioning console switch input operation signals on the guidance panel.Be arranged on various air conditioning console switch on the panel comprise console switch for the vehicle air adjuster, be used for setting vehicle interior temperature the vehicle interior temperature configuration switch and be used for the selector switch of select operating mode.The air conditioning controller comprises integral with one another for the control device of controlling the motor 11b that is used for compressor 11 and open/closed valve 15a etc., and the air conditioning controller is designed to control the operation of these parts.In the air conditioning controller of present embodiment, the structure (hardware and software) that is used for the operation of control compressor 11 is used as cold-producing medium discharge capacity control device.Each structure of installing the operation of 15a and 15b that is used for control formation refrigerant flowpath switching device shifter is used as the refrigerant flowpath control device.Be used for control and be formed for the structure of operation of triple valve 42 of cooling medium loop switching device shifter of cooling agent as the cooling medium circuit control device.The air conditioning controller of present embodiment comprises for basis determines from the detection signal of the above sensor groups that is used for air conditioning control whether frost is formed on the structure (device is determined in frosting) at outdoor heat converter 60 places.Particularly, when the speed of traveling vehicle is equal to or less than predetermined reference value (in the present embodiment, 20km/h) and the refrigerant temperature Te of the outlet side of outdoor heat converter 60 when being equal to or less than 0 ℃, the frosting of present embodiment determines that device determines to produce at outdoor heat converter 60 places frosting.Next, the operation of the automotive air conditioner 1 with the above structure in the present embodiment is below described.The automotive air conditioner 1 of present embodiment can be carried out for the heating operation of heating vehicle interior with for the cooling down operation that cools off vehicle interior.In heating operation, can also carry out the operation of defrost operation and Waste Heat Recovery.Next, below each operation of explanation.

(a) heating operation

When the console switch at guidance panel is opened under the situation of (ON) when selecting the heating operation pattern by selector switch the beginning heating operation.Then, in heating operation, when frosting determines that device determines that frost is formed on outdoor heat converter 60 places, carry out defrost operation.When being equal to or greater than predetermined reference temperature (in the present embodiment, 60 ℃) by coolant temperature sensor 52 detected coolant temperature Tw, carry out the Waste Heat Recovery operation.In the normal heating operation, the air conditioning controller cuts out open/closed valve 15a, and triple valve 15b is switched to the refrigerant flowpath that is connected to the entrance side of holder 18 for the outlet side with outdoor heat exchange department 60.Further, thereby controller actuating cooling medium pump 41 pushes cooling agent with predetermined amount of flow, and the triple valve 42 of coolant circulation circuit 40 is switched to for allowing cooling agent from the cooling medium loop of bypass by radiator 70.Like this, heat pump cycle 10 is switched to for allowing cold-producing medium along as by the refrigerant flowpath that flows shown in the filled arrows of Fig. 1.Coolant circulation circuit 40 also is switched to for allowing cold-producing medium along as by cooling medium flowing loop shown in the dotted arrow of Fig. 1.Air conditioning controller with above refrigerant flowpath and cooling medium loop reads from the detection signal of the above sensor groups that is used for air conditioning control with from the operation signal of guidance panel.According to detection signal and operation signal, calculate target outlet air temperature TAO as the target temperature that will be blown into the air in the vehicle interior.Further, according to the target outlet air temperature TAO that calculates with determine to be connected to the mode of operation of various air conditioning control assemblies of the outlet side of air conditioning controller from the detection signal of sensor groups.For example, the cold-producing medium discharge capacity of compressor 11, that is, the control signal that outputs to the motor of compressor 11 is determined by following.At first, determine the target evaporator outlet air temperature TEO of indoor evaporator 20 according to target outlet air temperature TAO with reference to being stored in control chart in the air conditioning controller in advance.

According to target evaporator outlet air temperature TEO and detected from the deviation between the blow air temperature of indoor evaporator 20 by evaporator temperature sensor, determine to be output to the control signal of the motor of compressor 11, thereby the blow air temperature by the air that utilizes feedback to make to blow from indoor evaporator 20 is near target evaporator outlet air temperature TEO.

According to the blow air temperature of target outlet air temperature TAO, indoor evaporator 20 with from the definite control signal that will be output to the servo motor of air mix door 34 of the temperature by the detected cold-producing medium of refrigerant emission temperature sensor that compressor 11 discharges, make the temperature that is blown into the air in the vehicle interior become the desired temperatures that the passenger uses the vehicle interior temperature configuration switch to set.

In normal heating operation, defrost operation and Waste Heat Recovery operating period, can control the aperture of air mix door 34, make the whole volume of the air from the vehicle interior that air blast 32 blows by indoor condenser 12.

Then, the control signal of determining as mentioned above is output to various air conditioning control assemblies.After this, up to by till the stopping of guidance panel request automotive air conditioner, control program repeats in each predetermined control circulation.Control program comprises a series of processing in the following order: the determining and the output of control voltage and control signal of the mode of operation of the reading of detection signal and operation signal, the calculating of target outlet air temperature TAO, various air conditioning control assemblies.This repetition of executive control program in the same way basically in other operator scheme.

In heat pump cycle 10, in normal heating operating period, flow into the indoor condenser 12 from the high-pressure refrigerant of compressor 11 dischargings.Flow into cold-producing medium in the indoor condenser 12 by indoor evaporator 20 and the heat of the vehicle interior air exchange heat that is blowed by air blast 32 with the dissipation cold-producing medium, make that the air in the compartment is heated.

Because open/closed valve 15a closes, therefore the high-pressure refrigerants that flow from indoor condenser 12 flow into heating with fixed restriction device 13 to be depressurized by throttling arrangement 13 and to expand.The low pressure refrigerant that is heated with 13 decompressions of fixed restriction device and expansion flow in the outdoor heat exchange department 60.The low pressure refrigerant that flow in the outdoor heat exchange department 60 absorbs heat from the extraneous air that is blowed by blower fan 17, and is evaporated.

At this moment, coolant circulation circuit 40 is switched to for allowing cooling agent from the cooling medium loop of bypass by radiator 70, thereby prevent that cooling agent from dissipating heat to the cold-producing medium that flows through outdoor heat exchange department 60, and prevent that cooling agent from absorbing heat from the cold-producing medium that flows through outdoor heat exchange department 60.That is, cooling agent has not a particle of heat affecting to the cold-producing medium that flows through outdoor heat exchange department 60.

Because triple valve 15b is switched to the refrigerant flowpath that the outlet side of outdoor heat exchange department 60 is connected to the entrance side of holder 18, therefore the cold-producing medium that flows from outdoor heat exchange department 60 flow into the holder 18 and is separated into liquid and gas.Being stored vapor phase refrigerant that device 18 separates is sucked by compressor 11 and is compressed again.

As mentioned above, in the normal heating operation, the air in the vehicle interior is heated by indoor condenser 12 by the heat that contains from the cold-producing medium of compressor 11 dischargings, thereby can carry out the heating operation of vehicle interior.

(b) defrost operation

Next, defrost operation is below described.Be used for by coming in the refrigerating circulatory device of vaporized refrigerant at outdoor heat exchange department 60 heat-shift between cold-producing medium and extraneous air, be similar to the heat pump cycle 10 of present embodiment, when becoming, the cold-producing medium evaporating temperature of outdoor heat exchange department 60 is equal to or less than the frosting temperature (particularly, 0 ℃) time, frost may be formed on outdoor heat exchange department 60 places.

So the frost that forms is closed the outside air opening 16a of heat exchanger 16 by frost, thereby reduces the heat-exchange capacity of outdoor heat exchange department 60 hastily.In the heat pump cycle 10 of present embodiment, when in heating operation, determining that by frosting device determines to produce frosting at outdoor heat exchange department 60 places, the beginning defrost operation.

In defrost operation, the air conditioning controller stops the operation of compressor 11, and the operation of the fan 17 that turns off the blast.Therefore, during defrost operation, compare with normal heating operation, thereby the flow that flow into the cold-producing medium in the outdoor heat exchange department 60 is reduced the volume (amount) to reduce to flow into the extraneous air among the outside air opening 16a.

The air conditioning controller switches to the triple valve 42 of coolant circulation circuit 40 for allowing cooling agent as by the cooling medium loop in the inflow radiator 70 shown in the dotted arrow of Fig. 2.Therefore, coolant circulation circuit 40 is switched to for making cold-producing medium as not making cold-producing medium cycle through heat pump cycle 10 by cooling medium flowing loop shown in the dotted arrow of Fig. 2.

Therefore, flow through the heat that contains in the cooling agent of cooling medium pipe 71 of radiator 70 and be delivered to outdoor heat exchange department 60 via outer fin 50, thereby carry out the defrost operation of outdoor heat exchange department 60.That is, flow through the cold-producing medium of heat exchanger 16 and the flow of extraneous air and be changed (reducing particularly) to use the used heat realization defrost operation of advancing with motor MG effectively.

(c) Waste Heat Recovery operation

Next, the Waste Heat Recovery operation is below described.Preferably, in order to suppress to advance overheated with motor MG, the temperature of cooling agent remained on predetermined upper limit temperature or below predetermined upper limit temperature.Further, in order to reduce owing to being sealed to the friction loss that the increase of advancing with the viscosity of the lubricating oil among the motor MG causes, preferably, the temperature of cooling agent is maintained at the predetermined lower bound temperature or more than the predetermined lower bound temperature.

In the heat pump cycle 10 of present embodiment, when coolant temperature Tw during heating operation is equal to or greater than predetermined reference temperature (60 ℃), carry out the Waste Heat Recovery operation.In defrost operation, the triple valve 15b of heat pump cycle 10 with normal heating operation in identical mode carry out, but the triple valve 42 of coolant circulation circuit 40 is switched to for making cooling agent as by the cooling medium loop that flow into shown in the dotted arrow of Fig. 3 in the radiator 70 in the mode identical with defrost operation.

Therefore, as by shown in the filled arrows among Fig. 3, in the mode identical with the normal heating operation, from the air of high pressure, high temperature refrigerant in indoor condenser 12 heating vehicle interiors of compressor 11 discharging, be heated with 13 decompressions of fixed restriction device then and expand to flow in the outdoor heat exchange department 60.

Because carrying out to, triple valve 42 is used for making cooling agent flow into the switching in the cooling medium loop of radiator 70, therefore flow into low pressure refrigerant in the outdoor heat exchange department 60 absorb contain in the heat that contains in the extraneous air that is blowed by blower fan 17 and the cooling agent and pass to the heat of cold-producing medium via outer fin 50, thereby be evaporated.Other operation is identical with other operation of normal heating operation.

As mentioned above, in Waste Heat Recovery operation, the air in the vehicle interior is heated by the heat from the cold-producing medium of compressor 11 dischargings at indoor condenser 12 places, thereby can carry out the heating of vehicle interior.At this moment, cold-producing medium not only absorbs the heat that contains in the extraneous air, and absorb contain in the cooling agent and pass to the heat of cold-producing medium via outer fin 50, realize the heating of vehicle interior with the used heat of motor MG thereby can use effectively to advance.

(d) cooling down operation

Open under the situation of (ON) when selecting the cooling down operation pattern by selector switch when the console switch at guidance panel, cooling down operation begins.In cooling down operation, air conditioning controller opens open/closed valve 15a, and triple valve 15b switched to for the outlet side with outdoor heat exchange department 60 be connected to cooling with the refrigerant flowpath of the entrance side of fixed restriction device 19.Therefore, heat pump cycle 10 is switched to for making cold-producing medium as by the refrigerant flowpath that flows shown in the filled arrows of Fig. 4.

At this moment, when coolant temperature Tw was equal to or greater than reference temperature, the triple valve 42 of coolant circulation circuit 40 was switched to for making cooling agent flow into the cooling medium loop of radiator 70.On the contrary, as coolant temperature Tw during less than predetermined reference temperature, triple valve 42 is switched to for allowing cooling agent from the cooling medium loop of bypass by radiator 70.The ANALYSIS OF COOLANT FLOW that obtains when coolant temperature Tw is equal to or greater than reference temperature is represented by the dotted arrow among Fig. 4.

In heat pump cycle 10, during cooling down operation, flow into the indoor condenser 12 from the high-pressure refrigerant of compressor 11 discharging, and with vehicle interior in by air blast 32 blow and the air exchange heat by indoor evaporator 20 with its heat that dissipates.Because open/closed valve 15a opens, therefore the high-pressure refrigerant that flows from indoor condenser 12 flow into outdoor heat exchange department 60 via fixed restriction with bypass passageways 14.Flow into low pressure refrigerant in the outdoor heat exchange department 60 further towards the extraneous air distribute heat that is blowed by blower fan 17.

Because triple valve 15b is switched to for the outlet side with outdoor heat exchange department 60 and is connected to cooling with the refrigerant flowpath of the entrance side of fixed restriction device 19, therefore the cold-producing mediums that flow from outdoor heat exchange department 60 are depressurized with fixed restriction device 19 by cooling and expand.Flow into the indoor evaporator 20 with the cold-producing medium that fixed restriction device 19 flows from cooling, and the absorption of air heat that is blowed by air blast 32 from vehicle interior is to be evaporated.Like this, the air in the vehicle interior can be cooled.

The cold-producing medium that flows from indoor evaporator 20 flow into the holder 18, is separated into liquid and gas by holder 18 then.Being stored device 18 gas separated cold-producing mediums is inhaled in the compressor 11 and by compressor 11 and compresses again.As mentioned above, during cooling down operation, indoor evaporator 20 place's low pressure refrigerants from vehicle interior the absorption of air heat and evaporate self, thereby therefore the air in the coolant compartment can be carried out the cooling of vehicle interior.

As mentioned above, the air regulator 1 that is used for vehicle in the present embodiment can carried out switching between the refrigerant flowpath of heat pump cycle 10 and between the cooling medium loop at coolant circulation circuit 40, thereby realizes various operations.Further, in the present embodiment, more than concrete heat exchanger 16 can be used between three kinds of fluids (that is, cold-producing medium, cooling agent and extraneous air), carrying out suitable heat exchange in each operation.

More specifically, the heat exchanger 16 of present embodiment comprises outer fin 50, and each is arranged on described outer fin 50 among the outside air opening 16a between the cooling medium pipe 71 of the refrigerant pipe 61 that is formed on outdoor heat exchange department 60 and radiator 70.This outer fin 50 can carry out heat transmission between refrigerant pipe 61 and cooling medium pipe 71.

Therefore, during defrost operation, the heat that contains in the cooling agent can be delivered to outdoor heat exchange department 60 via outer fin 50, thereby can use the used heat of advancing with motor MG so that outdoor heat exchange department 60 is defrosted effectively.

Further, in the present embodiment, during defrost operation, the operation of compressor 11 is stopped to reduce to flow into the flow of the cold-producing medium in the outdoor heat exchange department 60, thereby can prevent that the heat that passes to outdoor heat exchange department 60 from absorbing in the cold-producing medium that flows through refrigerant pipe 61 via outer fin 50 and refrigerant pipe 61.That is, can suppress heat exchange unnecessary between cooling agent and the cold-producing medium.

During defrost operation, the operation of blower fan 17 stops to reduce to flow into the volume (amount) of the extraneous air among the outside air opening 16a, thereby can prevent from being absorbed in the extraneous air that flows through outside air opening 16a via the heat that outer fin 50 passes to outdoor heat exchange department 60.That is, can suppress heat exchange unnecessary between cooling agent and the extraneous air.

In Waste Heat Recovery operating period, heat exchanger makes the used heat of advancing with motor MG to absorb in the cold-producing medium via refrigerant pipe 61, cooling medium pipe 71 and outer fin 50 heat-shift between cooling agent and cold-producing medium.In addition, heat exchanger is the heat-shift between cooling agent and extraneous air via cooling medium pipe 71 and outer fin 50 also, makes the unnecessary used heat of advancing with motor MG to be dispersed into extraneous air.

In normal heating operating period, heat exchanger is heat-shift between cold-producing medium and extraneous air via refrigerant pipe 61 and outer fin 50, makes that the heat of extraneous air can be absorbed in the cold-producing medium.In addition, in normal heating operating period, the triple valve 42 of coolant circulation circuit 40 is switched to for allowing cooling agent from the cooling medium loop of bypass by radiator 70, thereby can suppress heat exchange unnecessary between cooling agent and the extraneous air, be stored in the cooling agent with the used heat that will advance with motor MG, thereby promote to advance preheating with motor MG.

In the heat exchanger 16 of present embodiment, refrigerant pipe 61 and cooling medium pipe 71 are arranged between refrigerant side header tank 62 and the cooling medium side header tank 72, make each outside air opening 16a be formed by the space between refrigerant pipe 61 and the cooling medium pipe 71.Refrigerant side header tank 62 and cooling medium side header tank 72 are not arranged along the flow direction of extraneous air.Therefore, can prevent that whole heat exchanger 16 from increasing along the size of the flow direction of extraneous air.

In addition, the refrigerant side turning part 61e of refrigerant pipe 61 is oriented to compare more near cooling medium side header tank 72 with refrigerant side header tank 62.In addition, the cooling medium side turning part 71e of cooling medium pipe 71 is oriented to compare more near refrigerant side header tank 62 with cooling medium side header tank 72.The structure that refrigerant side header tank 62 is connected to refrigerant pipe 61 can have with cooling medium side header tank 72 and is connected to the identical shape of the shape of structure of cooling medium pipe 71.

In the present embodiment, the cooling medium side plate 73 of the cold-producing medium side plate 63 of refrigerant side header tank 62 and cooling medium side header tank 72 is provided with intercommunicating pore and other the closed intercommunicating pore that is communicated with refrigerant flowpath 61c and cooling medium flow path 71c respectively.Be used for the structure that refrigerant pipe 61 is connected to refrigerant side header tank 62 can being had and being used for that cooling medium pipe 71 is connected to the identical shape of the shape of structure of cooling medium side header tank 72, thereby can improve the productivity ratio of heat exchanger.

Therefore, the heat exchanger 16 of present embodiment do not need to increase improve under the situation of size can be between three kinds of fluids the productivity ratio of the heat exchanger of heat-shift.

In the heat exchanger 16 of present embodiment, refrigerant pipe 61 and cooling medium pipe 71 be fixed to refrigerant side header tank 62 and cooling medium side header tank 72 both, thereby can increase the mechanical strength of whole heat exchanger 16.Further, fin 50 is arranged in the interim process of outside air opening 16a outside, and outer fin 50 can be easily temporary fixed, can firmly fix after interim combination then.

The coolant channel area of the pars intermedia of each among refrigerant side turning part 61e and the cooling medium side turning part 71e is greater than the fluid inflow portion of corresponding turning part and each the fluid passage area in the fluid outflow portion.When cold-producing medium passes through refrigerant side turning part 61e, perhaps when cooling agent passes through cooling medium side turning part 71e, can reduce the pressure loss.

Be arranged in the inner space of the interior fin 65 of refrigerant pipe 61 and cooling medium pipe 71 inside and expansion section 61f that 75 end is projected into each turning

part

61e and 71e and 71f.Therefore, the part that

interior fin

65 and 75 wherein coated with solder tend to come off (for example,

interior fin

65 and 75 end) be not used as soldered surface interested, thus the binding deficient between the interior perimeter surface of each in each in the

fin

65 and 75 and refrigerant pipe 61 and the cooling medium pipe 71 in being easy to suppress.

Be similar to present embodiment, can be between three kinds of fluids in the heat exchanger 16 of heat-shift, based on operating condition, the temperature that is introduced in the cold-producing medium in the outdoor heat exchange department 60 be different from the temperature that is introduced in the cooling agent in the radiator 70 sometimes.In this case, the amount (thermal expansion amount) of the thermal strain that produces in the refrigerant pipe 61 is different from the amount of the thermal strain that produces in the cooling medium pipe 71, and this may cause the destruction of heat exchanger 16.

On the contrary, the heat exchanger 16 of present embodiment comprises and is arranged on alternately laminated with predetermined space or the refrigerant pipe 61 that piles up and the outer fin 50 between the cooling medium pipe 71.The heat exchange that each outer fin 50 promotes between extraneous air, cold-producing medium and cooling agents, thus the poor of thermal strain between the

pipe

61 and 71 alleviated.Therefore, the heat exchanger 16 of present embodiment can suppress the destruction that causes refrigerant pipe 61 and cooling medium pipe 71 owing to the thermal strain poor (thermal expansion amount) that produces between refrigerant pipe 61 and the cooling medium pipe 71.

In the heat exchanger 16 of present embodiment, the cooling medium pipe upstream portion 711 of cooling medium pipe 71 is positioned at upstream side with respect to cooling medium pipe downstream portion 712 along the flow direction A of extraneous air.Therefore, the temperature that flow into the cooling medium in the cooling medium pipe 71 therein is higher than under each the mode of operation of temperature in cold-producing medium and the extraneous air, thereby can guarantee that the temperature difference between cooling agent and the extraneous air is to increase the amount of heat dissipation at the upstream side of the cooling agent stream of cooling medium pipe 71.Therefore, it is poor that the temperature difference between cooling agent and the cold-producing medium can be reduced the thermal strain that alleviates between refrigerant pipe 61 and the cooling medium pipe 71.In this example, cooling agent is corresponding to " high temperature side fluid "; Cooling medium pipe 71 is corresponding to " high temperature side pipe "; The cooling medium pipe upstream portion 711 of cooling medium pipe 71 is corresponding to " high temperature side pipe upstream portion "; And the cooling medium pipe downstream portion 712 of cooling medium pipe 71 is corresponding to " high temperature side pipe downstream portion ".Cold-producing medium is corresponding to " low temperature side fluid "; Refrigerant pipe 61 is corresponding to " low temperature side pipe "; The refrigerant pipe upstream portion 611 of refrigerant pipe 61 is corresponding to " low temperature side pipe upstream portion "; And the refrigerant pipe downstream portion 612 of refrigerant pipe 61 is corresponding to " low temperature side pipe downstream portion ".

Second embodiment

In the present embodiment, the structure of the heat exchanger 16 of first embodiment is carried out some changes.Below use Figure 12-14 to describe the detailed construction of the heat exchanger 16 of present embodiment.

Figure 12 has shown the perspective view of the profile of the heat exchanger 16 among first embodiment.Figure 13 has shown for the cold-producing medium of explanation heat exchanger 16 and the perspective schematic view of flow of coolant.Figure 14 has shown the schematic part decomposition diagram of heat exchanger 16.Figure 12, Figure 13 and Figure 14 correspond respectively to Fig. 5, Figure 10 and Figure 11 of first embodiment.In Figure 12-14, represented by identical Reference numeral with the parts parts identical or that be equal to of first embodiment.This is equally applicable to following institute drawings attached.

As Figure 12 and shown in Figure 14, the refrigerant pipe 61 of present embodiment and each in the cooling medium pipe 71 form at the flat tube that the direction perpendicular to longitudinal direction has flat cross section by bending.More specifically, refrigerant pipe 61 be bent so that the flat surfaces of refrigerant pipe 61 toward each other, and cooling medium pipe 71 also be bent so that the flat surfaces of cooling medium pipe 71 toward each other.

Therefore, the cooling medium side turning part 71e of the refrigerant side turning part 61e of the refrigerant pipe in the present embodiment 61 and cooling medium pipe 71 is formed by the bend of

pipe

61 and 71 respectively.Outside air opening 16a in the present embodiment not only is formed between the flat surfaces of refrigerant pipe 61 flat surfaces relative with flat surfaces cooling medium pipe 71 and refrigerant pipe 61, but also is formed between the flat surfaces of relative refrigerant pipe 61 and between the flat surfaces of relative cooling medium pipe 71.

Outside air opening 16a is provided with the outer fin 50 identical with outer fin among first embodiment.Be similar to Figure 11, for the ease of understanding, Figure 14 has omitted the diagram of outer fin 50.

As shown in figure 14, refrigerant pipe 61 is arranged to two row along the flow direction A of extraneous air.An openend that is arranged on the refrigerant pipe 61 of downwind side is communicated with the allocation space 62b of refrigerant side header tank 62, and another pipe 61 the openend that is arranged on weather side is communicated with the collection space 62a of refrigerant side header tank 62.

The partition member (not shown) is arranged on refrigerant side header tank 62 inside.Another openend that partition member makes a described refrigerant pipe 61 that is arranged on downwind side with under the situation that collection space 62a and the allocation space 62b of refrigerant side header tank 62 inside are communicated be not communicated with another openend of another pipe 61 that is arranged on weather side.

As shown in figure 14, cooling medium pipe 71 is arranged to two row along the flow direction A of extraneous air.An openend that is arranged on the cooling medium pipe 71 of weather side is communicated with the allocation space 72b of cooling medium side header tank 72, and another pipe 71 the openend that is arranged on downwind side is communicated with the collection space 72a of cooling medium side header tank 72.

The partition member (not shown) also is arranged on cooling medium side header tank 72 inside.Another openend that partition member makes a described cooling medium pipe 71 that is arranged on weather side with under the situation that collection space 72a and the allocation space 72b of cooling medium side header tank 72 inside are communicated be not communicated with another openend of described another pipe 71 that is arranged on downwind side.

Therefore, as shown in figure 13, in the heat exchanger 16 of present embodiment, be introduced in cold-producing medium among the allocation space 62b of refrigerant side header tank 62 and flow in the refrigerant pipe 61 that is arranged on downwind side refrigerant side turning part 61e with the refrigerant pipe 61 by being arranged on downwind side, turn back to refrigerant side header tank 62 then.Then, cold-producing medium flow into the refrigerant pipe 61 that is arranged on weather side with the refrigerant side turning part 61e of the cold-producing medium side pipe 61 by being arranged on weather side, and derives from the collection space 62a of refrigerant side header tank 62.

On the contrary, be introduced in cold-producing medium among the allocation space 72b of cooling medium side header tank 72 and flow into the cooling medium side turning part 71e that is arranged in the weather side cooling medium pipe 71 with the cooling medium pipe 71 by being arranged on weather side, turn back to cooling medium side header tank 72 then.Then, cold-producing medium flow in the cooling medium pipe 71 that is arranged on downwind side the cooling medium side turning part 71e with the cooling medium side pipe 71 by being arranged on downwind side, and derives from the collection space 72a of cooling medium side header tank 72.

Comprise heat exchanger 16 heat pump cycle 10 other parts structure and operation and other parts of first embodiment structure and operate identical.Therefore, be similar to first embodiment, the heat exchanger 16 of present embodiment also can be at three kinds of fluids in each operation of heat pump cycle 10: carry out suitable heat exchange between cold-producing medium, cooling agent and the extraneous air.Present embodiment can also improve under the situation that does not increase size can be between three kinds of fluids the productivity ratio of the heat exchanger of heat-shift.

Further, the heat exchanger 16 of present embodiment uses the flat tube that can form with low cost by expressing technique or drawing process as refrigerant pipe 61 and cooling medium pipe 71.Therefore, present embodiment can further be boosted productivity.

The 3rd embodiment

In the mode of example, second embodiment uses and is bent to flat surfaces part flat tube respect to one another as refrigerant pipe 61 and cooling medium pipe 71.In the present embodiment, as shown in figure 15, each pipe all is bent, make among turning part 61e and the 71e each the flat surfaces of upstream side and each the flat surfaces in downstream among turning part 61e and the 71e in same plane, be arranged to two row along the flow direction A of extraneous air.

In Figure 15, (a) be the front view of the refrigerant pipe 61 (cooling medium pipe 71) of present embodiment, and (b) be the side view for the described pipe of cold-producing medium.Figure 15 (a) and 15 (b) are corresponding to Fig. 6 (a) and 6 (b) of first embodiment.Figure 15 (a) and 15 (b) have shown refrigerant pipe 61, and the while is represented by the respective drawings mark in the bracket corresponding to the parts of the cooling medium pipe 71 of the parts of refrigerant pipe 61.

Comprise heat exchanger 16 heat pump cycle 10 other parts structure and operation and other parts of first embodiment structure and operate identical.Therefore, be similar to first embodiment, the heat exchanger 16 of present embodiment also can be at three kinds of fluids in each operation of heat pump cycle 10: carry out suitable heat exchange between cold-producing medium, cooling agent and the extraneous air.Present embodiment also can improve under the situation that does not increase size can be between three kinds of fluids the productivity ratio of the heat exchanger of heat-shift.

Be similar to second embodiment, present embodiment also can be made refrigerant pipe 61 and cooling medium pipe 71 with low cost, therefore can further improve productive rate.

The 4th embodiment

In the present embodiment, shown in the configured in one piece figure of Figure 16, the structure of the heat pump cycle 10 of first embodiment is carried out some changes.Figure 16 has shown the configured in one piece figure of the refrigerant flowpath in the Waste Heat Recovery operation in the present embodiment.In the drawings, flowing of the cold-producing medium in the heat pump cycle 10 represented by solid line, and the flow of coolant in the coolant circulation circuit 40 is illustrated by the broken lines.

Particularly, in the present embodiment, the indoor condenser 12 of first embodiment is removed, and the outdoor heat exchange department 60 of first embodiment in the composite heat exchanger 16 is arranged in the housing 31 of room air regulon 30.Outdoor heat exchange department 60 in first embodiment in the composite heat exchanger 16 is as indoor condenser 12.Hereinafter, the part as indoor condenser 12 of heat exchanger 16 is called " indoor condenser ".

On the contrary, outdoor heat exchange department 60 is made of single heat exchanger, and described single heat exchanger is used for heat-shift between the cold-producing medium that flows through described heat exchanger and the extraneous air that blowed by blower fan 17.The structure of other parts in the present embodiment is identical with the structure of other parts of first embodiment.In the present embodiment, do not carry out defrost operation, but other operation is performed in the same manner as in the first embodiment.

Therefore, in the Waste Heat Recovery operating period of present embodiment, the air in the vehicle interior is by being heated with the cold-producing medium heat-shift that discharges from compressor 11 in the indoor evaporator of heat exchanger 16.Further, the air that is heated by indoor condenser in the vehicle interior can be by being heated with the cooling agent heat-shift in the radiator 70 of heat exchanger 16.

The structure of the heat pump cycle 10 of present embodiment can be in vehicle interior air and cooling agent between heat-shift.Even when heat pump cycle 10 (when) operation stops particularly, compressor 11, also can be realized the heating of vehicle interior.Even when the temperature of the cold-producing medium that discharges from compressor 11 heating efficiency low and heat pump cycle 10 is low, also can realize the heating of vehicle interior.

Apparently, disclosed heat exchanger 16 can be applied to the heat pump cycle 10 of present embodiment among second embodiment and the 3rd embodiment.

The 5th embodiment

In the present embodiment, the structure of the heat exchanger 16 of first embodiment is carried out some changes.Below use Figure 17 and 18 to describe the detailed construction of the heat exchanger 16 of present embodiment.

Figure 18 has shown the perspective view of the profile of the heat exchanger 16 in the present embodiment.Figure 18 is for the cold-producing medium of explanation heat exchanger 16 and the perspective schematic view of flow of coolant.Figure 17 and Figure 18 are corresponding to Fig. 5 and Figure 10 of first embodiment.For convenience of explanation, Figure 17 has omitted the

pipe

61 and 71 and the diagram of outer fin 50 of heat exchanger 16.

The outdoor heat exchange department 60 of the heat exchanger 16 of present embodiment comprises refrigerant side header tank 62, and described refrigerant side header tank 62 is made up of the

case

621 and 622 that the flow direction A along extraneous air is arranged to two row.First refrigerant case 621 that two flow directions along extraneous air of going casees 621 and 622 are arranged on upstream side is provided with partition member 621c, and described partition member 621c is arranged on the center along the longitudinal direction the inner space is separated into two space 621a and 621b.

First refrigerant case 621 is connected to and is arranged on the pipe of weather side along the flow direction A of extraneous air in a plurality of refrigerant pipe upstream portions 611 and the refrigerant pipe downstream portion 612.Case 621 usefulness act on collection and the distributor box of collecting and/or distributing the cold-producing medium that flows through pipe.

An end along the longitudinal direction of first refrigerant case 621 is connected to for the cold-producing medium inlet tube 64b that introduces cold-producing medium, and the other end along the longitudinal direction of refrigerant side case 64 is connected to for the cold-producing medium guide pipe 64c that derives and guide cold-producing medium.Cold-producing medium inlet tube 64b be formed on first refrigerant case 621 in two space 621a and the allocation space 621a among the 621b be communicated with.Cold-producing medium guide pipe 64c be formed on first refrigerant case 621 in two space 621a and the collection space 621b among the 621b be communicated with.

Be arranged to two row and be contained in the

case

621 and 622 in the refrigerant side header tank 62, second refrigerant case 622 that is arranged on the downstream along the flow direction A of extraneous air is connected to and is arranged on the pipe of downwind side along the flow direction A of extraneous air in a plurality of refrigerant pipe upstream portions 611 and the refrigerant pipe downstream portion 612.Second refrigerant case, 622 usefulness act on collection and the distributor box of collecting and/or distributing the cold-producing medium that flows through pipe.The two ends along the longitudinal direction of second refrigerant case 622 are by the enclosed member closure.

Be used for making and be introduced in one group of refrigerant pipe 61 that the flow of refrigerant of outdoor heat exchange department 60 passes through via cold-producing medium inlet tube 64b and form upstream side refrigerant pipe group 60a.Be used for making from the flow of refrigerant of upstream side refrigerant pipe group 60a and pass through to form downstream refrigerant pipe group 60b with one group of refrigerant pipe 61 of deriving from cold-producing medium guide pipe 64c.

In the refrigerant pipe 61 that forms upstream side refrigerant pipe group 60a, refrigerant pipe upstream portion 611 is arranged on upstream side with respect to refrigerant pipe downstream portion 612 along the flow direction A of extraneous air.In forming the refrigerant pipe 61 of downstream refrigerant pipe group 60b, refrigerant pipe upstream portion 611 is arranged on the downstream with respect to refrigerant pipe downstream portion 612 along the flow direction A of extraneous air.

In the outdoor heat exchange department 60 of present embodiment, as by shown in the filled arrows in the perspective schematic view of Figure 18, be introduced in cold-producing medium among the allocation space 621a of first refrigerant case 621 of header tank 62 via cold-producing medium inlet tube 64b and from upstream side refrigerant pipe group 60a, flow to refrigerant side turning part 61e along the be in the wind refrigerant pipe upstream portion 611 of side of flow of external air direction A.Cold-producing medium flows then and redirect to the outside empty air-flow direction A in edge among the upstream side refrigerant pipe group 60a at the refrigerant pipe downstream portion 612 of downwind side.Flow into cold-producing medium second refrigerant case 622 flowing in proper order with this and turn to the be in the wind refrigerant pipe downstream portion 612 of side of the outside empty air-flow direction A in edge among refrigerant side turning part 61e and the downstream refrigerant pipe group 60b at the refrigerant pipe upstream portion 611 of downwind side along the flow direction A of extraneous air from the refrigerant pipe group 60b of downstream from refrigerant pipe downstream portion 612.

Turn back to Figure 17, the radiator 70 of the heat exchanger 16 of present embodiment comprises cooling medium side header tank 72, and described cooling medium side header tank 72 is made up of the

case

721 and 722 that the flow direction A along extraneous air is arranged to two row.The first cooling medium case 721 that two flow directions along extraneous air of going casees 721 and 722 are arranged on upstream side is provided with partition member 721c, and described partition member 721c is arranged on the center along the longitudinal direction the inner space is separated into two spaces.

The first cooling medium case 721 is connected to and is arranged on the pipe of weather side along the flow direction A of extraneous air in a plurality of cooling medium pipe upstream portions 711 and the cooling medium pipe downstream portion 712.Case 721 usefulness act on collection and the distributor box of collecting and/or distributing the cooling medium that flows through pipe.

The first cooling medium case 721 end along the longitudinal direction is connected to for the cooling medium inlet tube 74b that introduces cooling medium, and cooling medium side case 74 other end along the longitudinal direction is connected to for deriving the also cooling medium guide pipe 74c of guided.Cooling medium inlet tube 74b be formed on the first cooling medium case 721 in two space 721a and the allocation space 721a among the 721b be communicated with.Cooling medium inlet tube 74c be formed on the first cooling medium case 721 in two space 721a and the collection space 721b among the 721b be communicated with.

Be arranged to two row and be contained in the

case

721 and 722 in the cooling medium side header tank 72, the second cooling medium case 722 that is arranged on the downstream along the flow direction A of extraneous air is connected to and is arranged on the pipe of downwind side along the flow direction A of extraneous air in a plurality of cooling medium pipe upstream portions 711 and the cooling medium pipe downstream portion 712.The second cooling medium case is with acting on collection and the distributor box of collecting and/or distributing the cooling medium that flows through pipe.The two ends along the longitudinal direction of the second cooling medium case 722 are by the enclosed member closure.

Be used for making and be introduced in one group of cooling medium pipe 71 that the cooling medium of radiator 70 flows through via cooling medium inlet tube 74b and form upstream side cooling medium pipe group 70a.Be used for making from the ANALYSIS OF COOLANT FLOW of upstream side cooling medium pipe group 70a and pass through to form downstream cooling medium pipe group 70b with another group cooling medium pipe 71 of deriving cooling agent from cooling medium guide pipe 74c.

In the cooling medium pipe 71 that forms upstream side cooling medium pipe group 70a, cooling medium pipe upstream portion 711 is arranged on upstream side with respect to cooling medium pipe downstream portion 712 along the flow direction A of extraneous air.In forming the cooling medium pipe 71 of downstream cooling medium pipe group 70b, cooling medium pipe upstream portion 711 is arranged on the downstream with respect to cooling medium pipe downstream portion 712 along the flow direction A of extraneous air.

In the radiator 70 of present embodiment, as by shown in the chain-dotted line in the perspective schematic view of Figure 18, be introduced in the be in the wind cooling medium pipe upstream portion 711 of side of the edge outside empty air-flow direction A of cooling medium from upstream side cooling medium pipe group 70a among the allocation space 721a of the first cooling medium case 721 of cooling medium side header tank 72 via cooling medium inlet tube 74b and flow to cooling medium side turning part 71e.Cooling medium flows then and redirect to the outside empty air-flow direction A in edge among the upstream side cooling medium pipe group 70a at the cooling medium pipe downstream portion 712 of downwind side.The flow direction A along extraneous air of cooling medium from the cooling medium pipe group 70b of downstream that flow into the second cooling medium case 722 from cooling medium pipe downstream portion 712 flow to cooling medium side turning part 71e at the cooling medium pipe upstream portion 711 of downwind side.Then, cooling medium flows and redirect among the cooling medium pipe group 70b of downstream the be in the wind cooling medium pipe downstream portion 712 of side along the flow direction A of extraneous air.

In the heat exchanger 16 of present embodiment, the cooling medium pipe upstream portion 711 of the refrigerant pipe upstream portion 611 of upstream side refrigerant pipe group 60a and upstream side cooling medium pipe group 70a is arranged in parallel along the stacked direction of pipe 61 and 71.In addition, the cooling medium pipe downstream portion 712 of the refrigerant pipe downstream portion 612 of upstream side refrigerant pipe group 60a and upstream side cooling medium pipe group 70a is arranged in parallel along the stacked direction of

pipe

61 and 71.

In the heat exchanger 16 of present embodiment, the cooling medium pipe upstream portion 711 of the refrigerant pipe upstream portion 611 of downstream refrigerant pipe group 60b and downstream cooling medium pipe group 70b is arranged in parallel along the stacked direction of pipe 61 and 71.In addition, the cooling medium pipe downstream portion 712 of the refrigerant pipe downstream portion 612 of downstream refrigerant pipe group 60b and downstream cooling medium pipe group 70b is arranged in parallel along the stacked direction of

pipe

61 and 71.

In outdoor heat exchange department 60, cold-producing medium flow direction along extraneous air in upstream side refrigerant pipe group 60a flow to upstream side from the downstream, and cold-producing medium flow direction along extraneous air in the refrigerant pipe group 60b of downstream flow to upstream side from the downstream.Similarly, in radiator 70, cooling agent flow direction along extraneous air in upstream side cooling medium pipe group 70a flow to the downstream from upstream side, and the flow direction along extraneous air flow to upstream side from the downstream in the cooling medium pipe group 70b of downstream.

Therefore, the refrigerant pipe 61 of formation upstream side refrigerant pipe group 60a and upstream side cooling medium pipe group 70a is designed to allow cold-producing medium to flow to downwind side from weather side along the flow direction A of extraneous air on identical direction with cooling medium pipe 71.The refrigerant pipe 61 that forms downstream refrigerant pipe group 60b and downstream cooling medium pipe 70b respectively and cooling medium pipe 71 are designed to allow cold-producing medium and cooling agent to flow to weather side from downwind side along the flow direction A of extraneous air on identical direction.

In addition, in the heat exchanger 16 of present embodiment, the refrigerant pipe upstream portion 611 that forms each refrigerant pipe 61 of upstream side refrigerant pipe group 60a is arranged on upstream side with respect to refrigerant pipe downstream portion 612 along the flow direction A of extraneous air.In addition, the cooling medium pipe upstream portion 711 that forms each cooling medium pipe 71 of upstream side cooling medium pipe group 70a is arranged on upstream side with respect to cooling medium pipe downstream portion 712 along the flow direction A of extraneous air.

Be introduced in the cold-producing medium in the outdoor heat exchange department 60 therein and be introduced under the mode of operation of temperature that cooling medium in the radiator 70 has the temperature that is higher than extraneous air, the temperature difference between cold-producing medium and the cooling agent reduces at the cold-producing medium upstream side of upstream side refrigerant pipe group 60a and the cooling agent upstream side of upstream side cooling medium pipe group 70a.In addition, can guarantee between cold-producing medium and the extraneous air and the temperature difference between cooling medium and the extraneous air, thereby can increase the amount of heat dissipation.Therefore, the thermal strain that can reduce between refrigerant pipe 61 and the cooling medium pipe 71 is poor.

In the heat exchanger 16 of present embodiment, the refrigerant pipe upstream portion 611 that forms each refrigerant pipe 61 of downstream refrigerant pipe group 60b is arranged on the downstream with respect to refrigerant pipe downstream portion 612 along the flow direction A of extraneous air.In addition, the cooling medium pipe upstream portion 711 that forms each cooling medium pipe 71 of downstream cooling medium pipe group 70a is arranged on the downstream with respect to cooling medium pipe downstream portion 712 along the flow direction A of extraneous air.

Cold-producing medium in being introduced in outdoor heat exchange department 60 and being introduced under the mode of operation of temperature that cooling medium in the radiator 70 has the temperature that is higher than extraneous air, the heat that contains in cold-producing medium and the cooling agent can fully be dissipated in the extraneous air in the cold-producing medium downstream of downstream refrigerant pipe group 60b and the cooling agent downstream of downstream cooling medium pipe group 70b.Therefore, can improve the performance of heat exchanger 16.

As finding out from the above description, the upstream side refrigerant pipe group 60a of present embodiment is corresponding to the upstream side first pipe group described in the claims.The downstream refrigerant pipe group 60b of present embodiment is corresponding to the downstream first pipe group.The upstream side cooling medium pipe group 70a of present embodiment is corresponding to the upstream side second pipe group described in the claim.The downstream cooling medium pipe group 70b of present embodiment is corresponding to the downstream second pipe group.

Other embodiment

The present invention is not limited to above embodiment, can carry out various modifications and change to disclosed embodiment under the situation that does not deviate from protection scope of the present invention and make.

(1) in above embodiment, in the mode of example, heat exchanger 16 has case and pipe in pipe structure, and described heat converter structure comprises two

heat exchange departments

60 and 70 with pipe (61,71) and collecting box and distributor box (62,72).The structure of each in the

heat exchange department

60 and 70 is not subject to this.

Alternatively, for example, heat exchanger can adopt usually said pull and stretch cup (drawn cup) formula heat converter structure, and described heat converter structure comprises via the stacked multi-disc plate of outer fin 50.Each plate all comprises pipe and the case that is communicated with pipe, and described pipe and case form by the pair of plate-shaped member that is aligned with each other in conjunction with each center.

In the cup type heat converter structure of this pull and stretch, the stacked so that case of plate of plate interconnects, thereby can form corresponding to each the structure in the refrigerant side header tank 62 in above-described embodiment and the cooling medium side header tank 72.

(2) in above embodiment, in the mode of example,

plate

63 and 73 is connected to

case

64 and 74 respectively, thereby the inner space is separated into

collection space

62a and 72a and

allocation space

62b and 72b, thereby to form refrigerant side header tank 62 and cooling medium side header tank 72.

Header tank

62 and 72 structure are not subject to this.

For example, header tank can be made up of two pipes, and the inner space of each pipe can be collection space or allocation space.This can improve the resistance to pressure of each header tank.

In above embodiment, in the mode of example, refrigerant pipe 61 and cooling medium pipe 71 are alternately laminated or pile up.Yet the structure of refrigerant pipe 61 and cooling medium pipe 71 is not subject to this.

For example, in the heat exchanger 16 of first embodiment and the 3rd embodiment, shown in Figure 19 (a), a plurality of (N) refrigerant pipe 61 can be stacked continuously, then a plurality of (M) cooling medium pipe 71 can be stacked continuously.At this moment, the quantity of refrigerant pipe 61 can equal or be different from the quantity that pantostrat is stacked in the cooling medium pipe 71 on this refrigerant pipe 61.

For example, in the heat exchanger 16 of second embodiment, shown in Figure 19 (b)-19 (d), refrigerant pipe 61 can be positioned at upstream side with respect to the flow direction A of extraneous air, and cooling medium pipe 71 can be positioned at the downstream.

Figure 19 (a)-19 (d) has schematically shown the header tank cutaway view in a longitudinal direction of heat exchanger 16.In Figure 19 (a)-19 (d), for the ease of understanding, refrigerant pipe 61 represents to have the shadow region that by hatching cooling medium pipe 71 is represented by drawing the dotted line hachure.

In the structure that comprises refrigerant pipe placed adjacent one another 61 or cooling medium pipe 71 placed adjacent one another, shown in Figure 19 (a)-19 (d), outer fin 50 can be arranged between the adjacent refrigerant pipe 61 and in the space between the adjacent cooling medium pipe 71 ideally.

Like this, outer fin 50 be arranged between each and adjacent refrigerant pipe 61 or the cooling medium pipe 71 that is formed in the

pipe

61 and 71 have living space.Therefore, outer fin 50 promotes extraneous airs and flows through the heat exchange of managing between 61 and 71 the fluid (cold-producing medium or cooling agent), and the thermal strain that can alleviate between (reducing) refrigerant pipe 61 and the cooling medium pipe 71 is poor.Therefore, the destruction that can suppress heat exchanger 16.

(4) in above first embodiment, mode with example, the cooling medium pipe upstream portion 711 of the cooling medium pipe 71 in refrigerant pipe 61 and the cooling medium pipe 71 is positioned at upstream side with respect to cooling medium pipe downstream portion 712 along the flow direction A of extraneous air, and this does not limit the present invention.

For example, the refrigerant pipe upstream portion 611 of the refrigerant pipe 61 in refrigerant pipe 61 and the cooling medium pipe 71 can be positioned at upstream side along the flow direction A of extraneous air with respect to refrigerant pipe downstream portion 612.

Cold-producing medium in being introduced in outdoor heat exchange department 60 has under each the mode of operation of temperature of temperature that is higher than in cooling medium and the extraneous air, can guarantee that the temperature difference between cold-producing medium and the extraneous air is to increase the amount of heat dissipation at the upstream side of the cold-producing medium stream of refrigerant pipe 61.Therefore, can reduce the temperature difference between cold-producing medium and the cooling agent, this thermal strain that can reduce between refrigerant pipe 61 and the cooling medium pipe 71 is poor.In this example, cold-producing medium is corresponding to " high temperature side fluid "; Refrigerant pipe 61 is corresponding to " high temperature side pipe "; The refrigerant pipe upstream portion 611 of refrigerant pipe 61 is corresponding to " high temperature side pipe upstream portion "; And the refrigerant pipe downstream portion 12 of refrigerant pipe 61 is corresponding to " high temperature side pipe downstream portion ".Cooling agent is corresponding to " low temperature side fluid "; Cooling medium pipe 71 is corresponding to " low temperature side pipe "; The cooling medium pipe upstream portion 711 of cooling medium pipe 71 is corresponding to " low temperature side pipe upstream portion "; And the cooling medium pipe downstream portion 712 of cooling medium pipe 71 is corresponding to " low temperature side pipe downstream portion ".

(5) in above first embodiment, the cooling medium pipe downstream portion 712 of the refrigerant pipe upstream portion 611 of refrigerant pipe 61 and cooling medium pipe 71 is arranged along the stacked direction of pipe 61 and 71.In addition, in the mode of example, refrigerant pipe downstream portion 612 and cooling medium pipe upstream portion 711 are arranged along the stacked direction of pipe 61 and 71.The present invention is not limited to above structure.

For example, the cooling medium pipe upstream portion 711 of the refrigerant pipe upstream portion 611 of refrigerant pipe 61 and cooling medium pipe 71 can be arranged along the stacked direction of

pipe

61 and 71, and refrigerant pipe downstream portion 612 and cooling medium pipe downstream portion 712 can be arranged along the stacked direction of

pipe

61 and 71.

In this structure, the cold-producing medium that flows through refrigerant pipe 61 has reciprocal flow direction with the cooling agent that flows through cooling medium pipe 71 along each longitudinal direction of managing 61 and 71, and (for example has identical flow direction along the flow direction of extraneous air, from the weather side to the downwind side, perhaps from the downwind side to the weather side) (this is the partial parallel flow structure).

Compare with the heat exchanger 16 of first embodiment, the heat exchanger 16 with this structure reduces heat-exchange capacity, but can reduce to flow through the cold-producing medium of refrigerant pipe 61 on the whole and flow through the temperature difference between the cooling medium of cooling medium pipe 71.

With reference to Figure 20, below be to flow through the cold-producing medium of refrigerant pipe 61 and flow through the reason that the temperature difference between the cooling medium of cooling medium pipe 71 can be reduced in the heat exchanger 16 with partial parallel flow structure.Figure 20 is for the exemplary diagram of the architectural difference of explanation between various types of heat exchangers to the influence of the cold-producing medium of each pipe and the temperature difference between the cooling agent.In Figure 20, solid line schematically shows the variation of temperature of the high temperature fluid (high temperature side fluid) of cold-producing medium and cooling agent (represent inflow portion by dark circles, and represent outflow portion by the black diamonds piece).Chain-dotted line is shown schematically in the variation of temperature of cryogen in the heat exchanger 16 with partial parallel flow structure (low temperature side fluid).Double dot dash line schematically shows the variation of temperature of the cryogen in the reverse flow structure (heat exchanger 16 described in first embodiment).Chain-dotted line and double dot dash line show the variation of temperature under the following condition respectively.Externally the temperature of air is lower than under each the mode of operation of temperature in cold-producing medium and the cooling agent, use heat exchanger 16 with partial parallel flow structure from the outflow temperature T l2 that manages mobile low temperature side liquid with use the heat exchanger 16 with reverse flow structure identical from the outflow temperature T l2 ' of the low temperature side fluid of pipe outflow.

As mentioned above, the heat exchanger 16 with partial parallel flow structure is compared with the heat exchanger 16 described in first embodiment and is had the heat-exchange capacity that reduces.As by shown in the chain-dotted line and double dot dash line among Figure 20, in the heat exchanger 16 with partial parallel flow structure, the inflow temperature T l1 that flow into the low temperature side fluid in the pipe becomes and is higher than the inflow temperature T l1 ' of the low temperature side fluid in the heat exchanger 16 that flow into first embodiment.

That is, the temperature difference T ' between the inflow temperature T l1 ' of the inflow temperature T h1 ' of the high temperature side fluid in the temperature difference T between the inflow temperature T l1 of the inflow temperature T h1 that flow into the high temperature side fluid in the heat exchanger 16 with partial parallel flow structure and low temperature side liquid and the heat exchanger 16 that flow into first embodiment and low temperature side liquid compares less.

Therefore, compare with the heat exchanger 16 of first embodiment, the heat exchanger 16 with partial parallel flow structure can reduce to flow through the cold-producing medium of refrigerant pipe 61 on the whole and flow through the temperature difference between the cooling medium of cooling medium pipe 71.Therefore, the heat exchanger thermal strain that can reduce between refrigerant pipe 61 and the cooling medium pipe 71 is poor.The temperature that present embodiment is applied to extraneous air is lower than each the mode of operation of temperature in cold-producing medium and the cooling agent, but has the heat exchanger 16 of partial parallel flow structure no matter the relation between the temperature of the temperature of extraneous air and cold-producing medium and cooling agent can have following effect.That is, compare with the heat exchanger 16 of first embodiment, the heat exchanger 16 with partial parallel flow structure can reduce to flow through the cold-producing medium of refrigerant pipe 61 on the whole and flow through the temperature difference between the cooling medium of cooling medium pipe 71.

Further, in the heat exchanger 16 with partial parallel flow structure, refrigerant pipe upstream portion 611 and cooling medium pipe upstream portion 711 are positioned at upstream side with respect to refrigerant pipe downstream portion 612 and cooling medium pipe downstream portion 712 along the flow direction of extraneous air ideally.

Cold-producing medium in being introduced in outdoor heat exchange department 60 and being introduced under the mode of operation of temperature that cooling medium in the radiator 70 has the temperature that is higher than extraneous air, heat exchanger can be guaranteed between cold-producing medium and the extraneous air and the temperature difference between cooling agent and the extraneous air, thereby increases the amount of heat dissipation.Therefore, can reduce thermal strain difference between refrigerant pipe 61 and the cooling medium pipe 71 to suppress the destruction of heat exchanger 16.

(6) in above first embodiment, the cold-producing medium of heat pump cycle 10 is as first fluid, and the cooling agent of coolant circulation circuit 40 is used as second fluid, and is used as the 3rd fluid by the extraneous air that blower fan 17 blows, but first to the 3rd fluid is not subject to this.For example, be similar to the 3rd embodiment, the air in the vehicle interior can be used as the 3rd fluid.

For example, first fluid can be high-pressure side cold-producing medium or the low-pressure side cold-producing medium in the heat pump cycle 10.

For example, second fluid can be for cooling such as engine or be used for the cooling agent of supply of electric power to the electric device of the transverter of the usefulness motor MG that advances.Alternatively, second fluid can be that second heat exchange department can be used as oil cooler for the oil of cooling, and second fluid that uses can be heat accumulation agent, cold storage agent etc.

First to the 3rd fluid is not limited to the fluid that characteristic or composition differ from one another.Even first to the 3rd fluid can be temperature or the different fluid of state (for example gas phase or liquid phase) when these fluids have identical characteristics or composition.For example, the first fluid of use can be the high-pressure side cold-producing medium in the heat pump cycle 10, and second fluid that uses can be the low-pressure side cold-producing medium in the heat pump cycle 10.For example, when heat exchanger is provided with the circulate coolant that is suitable for being used in cooled engine and be used in the different circuit of circulate coolant of cooling transverter, the first fluid that uses is the cooling agent for engine, and second fluid that uses is the cooling agent for transverter.

Ideally, the relation between the temperature of first to the 3rd fluid is as follows: the temperature of the 3rd fluid is lower than the temperature of a fluid (high temperature side fluid) that has higher temperature in first fluid and second fluid and is higher than the temperature of another fluid (low temperature side fluid) with lower temperature.This temperature relation reduces the temperature of high temperature side fluid and increases the temperature of low temperature side fluid in heat exchanger 16, thereby can reduce the temperature difference between first fluid and second fluid.Therefore, thus can reduce to manage thermal strain difference between 61 and 71 to suppress the destruction of heat exchanger 16 effectively.

When the heat pump cycle 10 of using heat exchanger 16 of the present invention was used for fixed air adjuster, refrigerator, the cooling that is used for automatic vending machine and heater etc., second fluid can be for cooled engine with as the motor of the drive source of the compressor of heat pump cycle 10 and the cooling agent of other electric device.

In above embodiment, in the mode of example, heat exchanger 16 of the present invention is applied to heat pump cycle (kind of refrigeration cycle).The application of heat exchanger 16 of the present invention is not subject to this.That is, heat exchanger 16 of the present invention can be widely applied to any device for heat-shift between three kinds of fluids etc.

(7) in above embodiment, in the mode of example, the refrigerant pipe 61 of outdoor heat exchange department 60, the cooling medium pipe 71 of radiator 70 and outer fin 50 are formed by aluminium alloy (metal) and soldering is in the same place.Outer fin 50 can be formed by the material with fabulous thermal conductivity (for example, CNT etc.), and can be by any coupling apparatus combination such as adhesive etc.

Figure 21 has schematically shown the part perspective view according to the heat exchanger 16 of another embodiment.Figure 22 (a), 22 (b) and 22 (c) are the key diagrams for explanation outer fin 50 in another embodiment.Figure 22 (a) is the part front view of outer fin 50, and Figure 22 (b) is the cutaway view that the line XXIIB-XXIIB along Figure 22 (a) intercepts; And Figure 22 (c) is the enlarged drawing of the XXIIC part of Figure 22 (a).

Outside being similar to above each embodiment fin 50 and

pipe

61 and 71 in conjunction with the time, shown in Figure 21,22 (a), 22 (b) and 22 (c), outer fin 50 is provided with ideally for a plurality of slit 50a of the rigidity of the outer fin 50 of weakening partly.Slit 50a can be formed by the through hole that runs through outer fin 50 or the otch that is formed on the neighboring of outer fin 50.

Therefore, when having the thermal strain difference between

pipe

61 and 71, each slit 50a of outer fin 50 can the stress of absorption on pipe 61 and 71.Further, when the thermal strain difference generation of pipe between 61 and 71, has the outer fin 50 of slit 50a can suppress heat exchanger 16 in the part scope destruction.

(8) in above first embodiment, in the mode of example, in pipe and the temporary fixed step of case, refrigerant pipe 61 and cooling medium pipe 71 and the

interior fin

65 and 75 temporary fixed being in the same place that are stuck among

plate

61a, 61b, 71a and the 71b.Alternatively,

plate

61a, 61b, 71a and 71b can be provided with the location division for

interior fin

65 and 75.

This location division can by for example from refrigerant flowpath 61c, cooling medium flow path 71c, turning

part

61e and 71e and

expansion section

61f and 71f inwardly outstanding protuberance form.

(9) above second embodiment and the 3rd embodiment do not describe the

interior fin

65 and 75 that is arranged on refrigerant pipe 61 and cooling medium pipe 71 inside.Yet,

fin

65 and 75 time in expectation is adopted, flat tube is bent, and fin inserts in each the upstream side and the fluid flow path in downstream among turning part 61e and the 71e ideally then.Therefore, fin distortion in can preventing when the bending flat pipe.

(10) in above embodiment, in the mode of example, adopt electric T-shaped valve 42 as the loop switching device shifter that is used between the cooling medium loop of coolant circulation circuit 40, switching.Yet the loop switching device shifter is not subject to this.For example, can adopt thermostatic valve.Thermostatic valve is the coolant temperature responsive valves that is made of mechanical system, and described mechanical system is designed to by utilizing volume to make valve body move to open and close coolant guiding channel based on the hot wax (temperature-sensitive member) of variations in temperature.Therefore, can use thermostatic valve to remove coolant temperature sensor 52.

(11) though in above embodiment, in the mode of example, the cold-producing medium of use is common fluorine-based cold-producing medium, and the kind of cold-producing medium is not subject to this.The cold-producing medium that uses can be the natural refrigerant such as carbon dioxide or alkyl cold-producing medium.Further, heat pump cycle 10 can be the supercritical refrigeration cycle that wherein is equal to or higher than the critical pressure of cold-producing medium from the pressure of the cold-producing medium of compressor 11 discharging.

With reference to preferred embodiment the present invention is disclosed.Yet, should be understood that the present invention is not limited to above preferred embodiment and said structure.The present invention is intended to contain various modified example and equivalent structure thereof.In addition, with respect to disclosed embodiment comprise an other element or neither one element other preferred embodiment or various other combinations of each embodiment also fall in protection scope of the present invention and the spirit.

Claims

1. heat exchanger comprises:

First heat exchange department (60), described first heat exchange department comprises a plurality of first pipes (61) that first fluid flows through and extends to collect or distribute first case (62) of the first fluid that flows through described first pipe (61) at the stacked direction of described first pipe (61), described first heat exchange department (60) be suitable for described first fluid with at described first pipe (61) heat-shift between mobile the 3rd fluid on every side; With

Second heat exchange department (70), described second heat exchange department comprises a plurality of second pipes (71) that second fluid flows through and second case (72) that flows through second fluid of described second pipe (71) in the stacked direction extension of described second pipe (71) with collection or distribution, described second heat exchange department (70) is suitable for managing heat-shift between described the 3rd fluid that (71) flows on every side at described second fluid and described second, wherein:

Described first pipe (61) and described second pipe (71) are arranged between described first case (62) and described second case (72),

In described first pipe (61) at least one is arranged between described second pipe (71),

In described second pipe (71) at least one is arranged between described first pipe (61),

Be formed on the 3rd fluid passage (16a) that described the 3rd fluid of space boundary between described first pipe (61) and described second pipe (71) flows through,

Outer fin (50) is arranged in described the 3rd fluid passage (16a), to promote described first heat exchange department (60) and described second heat exchange department (70) heat exchange between the two, simultaneously can between the first fluid that flows through described first pipe (61) and second fluid that flows through described second pipe (71), carry out the heat transmission

Described first pipe (61) is provided with first turning part (61e) for the flow direction that changes described first fluid,

Described second pipe (71) is provided with second turning part (71e) for the flow direction that changes described second fluid,

Described first turning part (61e) is oriented to than close more described second case (72) of described first case (62), and

Described second turning part (71e) is oriented to than described second case (72) more near described first case (62).

2. heat exchanger according to claim 1, wherein:

The temperature that is introduced in the first fluid in described first heat exchange department (60) is different with the temperature of second fluid in being introduced in described second heat exchange department (70), and

Described outer fin (50) is arranged on and is formed between described first pipe (61) adjacent one another are and described second pipe (72), between adjacent described first pipe (61) and in the described second adjacent space of managing between (71).

3. heat exchanger according to claim 1 and 2, wherein, described first pipe (61) and described second manage (71) be fixed to described first case (62) and described second case (72) both.

4. according to each described heat exchanger among the claim 1-3, wherein, first fluid in being introduced in described first heat exchange department (60) and be introduced in a fluid that has higher temperature in second fluid in described second heat exchange department (70) and be defined as the high temperature side fluid, the upstream portion with respect to a corresponding turning part in described first turning part (61e) and described second turning part (71e) of the high temperature side pipe that the high temperature fluid in described first pipe (61) and described second pipe (71) flows through is defined as high temperature side pipe upstream portion, and described first pipe (61) and the described second downstream sidepiece with respect to a corresponding turning part in described first turning part (61e) and described second turning part (71e) of managing the high temperature side pipe that the high temperature fluid in (71) flows through is when being defined as high temperature side pipe downstream portion, the temperature of described the 3rd fluid is lower than the temperature of described high temperature side fluid, and at least one the high temperature side pipe upstream portion in the described high temperature side pipe is positioned at upstream side with respect to described high temperature side pipe downstream portion along the flow direction of described the 3rd fluid.

5. heat exchanger according to claim 4, wherein, first fluid in being introduced in described first heat exchange department (60) and be introduced in a fluid that has lower temperature in second fluid in described second heat exchange department (70) and be defined as the low temperature side fluid, the upstream portion with respect to the corresponding turning part in described first turning part (61e) and described second turning part (71e) of the low temperature side pipe that the low temperature side fluid in described first pipe (61) and described second pipe (71) flows through is defined as low temperature side pipe upstream portion, and when described first pipe (61) and described second manage low temperature side pipe that the cry-fluid flow in (71) passes through with respect to described first turning part (61e) and described second turning part (71e) in the downstream sidepiece of a corresponding turning part when being defined as low temperature side pipe downstream portion, the temperature of described the 3rd fluid is lower than the temperature of described low temperature side fluid, and at least one the low temperature side pipe upstream portion in the described low temperature side pipe is positioned at upstream side with respect to described low temperature side pipe downstream portion along the flow direction of described the 3rd fluid.

6. according to each described heat exchanger among the claim 1-4, wherein, the temperature of described the 3rd fluid is lower than the first fluid that is introduced in described first heat exchange department (60) and is introduced in the temperature of a fluid that has higher temperature in second fluid in described second heat exchange department (70) and is higher than the temperature of another fluid with lower temperature.

7. according to each described heat exchanger among the claim 1-3, wherein,

When described first upstream portion with respect to described first turning part (61e) of managing (61) is defined as the first pipe upstream portion (611), the downstream sidepiece with respect to described first turning part (61e) of described first pipe (61) is defined as the first pipe downstream portion (612), the upstream portion with respect to described second turning part (71e) of described second pipe (71) is defined as the second pipe upstream portion (711), and the downstream sidepiece with respect to described second turning part (71e) of described second pipe (71) is defined as the second pipe downstream portion when (712), the described first pipe upstream portion (611) and described second is managed upstream portion (711) along the stacked direction layout of described first pipe (61) and described second pipe (71), and the described first pipe downstream portion (612) and described second is managed downstream portion (712) along the stacked direction layout of described first pipe (61) and described second pipe (71).

8. heat exchanger according to claim 7, wherein, the described first pipe upstream portion (611) and the described second pipe upstream portion (711) are managed downstream portion (712) with respect to the described first pipe downstream portion (612) and described second and are positioned at upstream side along the flow direction of described the 3rd fluid.

9. heat exchanger according to claim 7, wherein:

Described first pipe (61) comprises the upstream side first pipe group (60a) and the downstream first pipe group (60b), the first fluid that wherein is introduced in described first heat exchange department (60) flows in the described upstream side first pipe group, the first fluid mobile from the described upstream side first pipe group (60a) flows so that described first fluid flows out described first heat exchange department (60) the first pipe group of described downstream

Described second pipe (71) comprises the upstream side second pipe group (70a) and the downstream second pipe group (70b), second fluid that wherein is introduced in described second heat exchange department (70) flows in the described upstream side second pipe group, second fluid mobile from the described upstream side second pipe group (70a) flows so that described second fluid flows out described second heat exchange department (70) the second pipe group of described downstream, and

The described first pipe upstream portion (611) of the described upstream side first pipe group (60a) and the described upstream side second pipe group (70a) and the described second pipe upstream portion (711) are managed downstream portion (712) with respect to the described first pipe downstream portion (612) and described second and are positioned at upstream side along the flow direction of described the 3rd fluid.

10. heat exchanger according to claim 9, wherein, the described first pipe upstream portion (611) of the described downstream first pipe group (60b) and the described downstream second pipe group (70b) and the described second pipe upstream portion (711) are managed downstream portion (712) with respect to the described first pipe downstream portion (612) and described second and are positioned at the downstream along the flow direction of described the 3rd fluid.

11. according to each described heat exchanger among the claim 1-10, wherein, described outer fin (50) is connected to described first pipe (61) and described second pipe (71), and is provided with a plurality of slits (50a) for the rigidity that weakens described outer fin partly.

12. according to each described heat exchanger among the claim 1-11, wherein, the area of the coolant channel of the pars intermedia of at least one in described first turning part (61e) and described second turning part (71e) is greater than the fluid inflow portion of a described turning part and each the area of fluid passage in the fluid outflow portion.

13. according to each described heat exchanger among the claim 1-12, also comprise:

It is interior to promote the heat exchange between described first fluid or described second fluid and described the 3rd fluid, wherein that interior fin (65,75), described interior fin are arranged on described first at least one of managing in (61) and described second pipe (71):

Fin (65,75) has the end in the inner space that is projected into described first turning part (61e) or described second turning part (71e) in described.

14. according to each described heat exchanger among the claim 1-13, wherein, described first pipe (61) and described second pipe each in (71) all by pass through in conjunction with a pair of plate (61a, 61b, 71a, 71b) the plate pipe of Xing Chenging is made.

15. according to each described heat exchanger among the claim 1-13, wherein, described first pipe (61) and described second each of managing in (71) all form by the bending flat pipe, and described flat tube has flat cross section in the direction perpendicular to the longitudinal direction of described flat tube.