JP5983387B2 - Heat exchanger - Google Patents

Description

  The present invention relates to a composite heat exchanger configured to be able to exchange heat between three types of fluids.

  Conventionally, a composite heat exchanger configured to be able to exchange heat between three kinds of fluids is known. For example, in Patent Document 1, heat is generated between three types of fluids: a refrigerant in a vapor compression refrigeration cycle (first fluid), cooling water for cooling an engine (second fluid), and outdoor air (third fluid). A composite heat exchanger configured to be replaceable is disclosed.

  Specifically, the heat exchanger of Patent Document 1 is configured by stacking and arranging a refrigerant tube through which a refrigerant flows and a cooling water tube through which cooling water flows to exchange heat between the refrigerant and outdoor air. And a heat exchanging section for exchanging heat between the cooling water and the outdoor air. An outer fin that allows heat transfer between the refrigerant flowing through the refrigerant tube and the cooling water flowing through the cooling water tube is disposed in the outdoor air passage formed between the adjacent tubes of the heat exchange unit. This realizes heat exchange between the refrigerant and the cooling water.

  Furthermore, the heat exchanger of Patent Document 1 includes an upstream heat exchange unit disposed on the upstream side in the outdoor air flow direction and a downstream heat exchange unit disposed on the downstream side in the outdoor air flow direction as heat exchange units. And the heat exchange amount between three types of fluids is adjusted by making the number ratio of the tube for refrigerants and the tube for cooling water in each heat exchange part into a different value.

JP 2012-225634 A

  However, as in the heat exchanger of Patent Document 1, if the number ratio of the refrigerant tubes and the cooling water tubes in the upstream heat exchange section and the downstream heat exchange section is different, the refrigerant in the upstream heat exchange section The stacking order of the tubes for cooling and the tubes for cooling water and the stacking order of the tubes for refrigerant and the cooling water in the downstream heat exchange section are different.

  For this reason, when both the refrigerant tank space for collecting or distributing the refrigerant and the cooling water tank space for collecting or distributing the cooling water are formed in the same tank portion, each refrigerant tube and the refrigerant are formed in the tank portion. The structure of the refrigerant flow path (refrigerant communication path) that communicates with the tank space for cooling, and the cooling water flow path (cooling water communication path) that communicates between each cooling water tube and the cooling water tank space are complicated. It is easy to end up.

  Therefore, in the heat exchanger of Patent Document 1, when viewed from the longitudinal direction of the refrigerant tube and the cooling water tube, the space in the tank portion arranged to overlap with the fluid inlet / outlet of both tubes is divided into members. The configuration is divided into two spaces. Then, one of the divided spaces is communicated with each refrigerant tube as a refrigerant tank space, and the other space is communicated with each cooling water tube as a cooling water tank space.

  However, as in Patent Document 1, when two spaces simply divided by the dividing member are used as a refrigerant tank space and a cooling water tank space, respectively, the refrigerant flowing into the refrigerant tank space and the cooling water tank There is a possibility that the cooling water flowing into the space may perform unnecessary heat exchange via the dividing member.

  For example, when the heat exchanger of Patent Document 1 is used as a heat-dissipating heat exchanger that dissipates heat from the refrigerant and cooling water to the outdoor air, the cooled refrigerant is unnecessary with the cooling water via the dividing member. There is a possibility that the enthalpy of the refrigerant increases due to heat exchange. Furthermore, such an increase in the enthalpy of the refrigerant causes a deterioration in the coefficient of performance of the refrigeration cycle.

  In view of the above points, a first object of the present invention is to easily form a fluid flow path formed in a tank portion in a heat exchanger configured to be able to exchange heat between three types of fluids.

  A second object of the present invention is to suppress unnecessary heat exchange between fluids in a tank part in a heat exchanger configured to be able to exchange heat between three types of fluids.

The present invention has been devised to achieve the above object. In the invention according to claim 1, the first tube (16a) through which the first fluid flows and the second tube through which the second fluid flows ( 43a) are arranged in a stack, heat exchange portions (71, 72) for exchanging heat between the first fluid and the third fluid and for exchanging heat between the second fluid and the third fluid, and a first tube ( A tank portion (73) in which tank spaces (73a to 73c) for collecting or distributing either one of the first fluid flowing through 16a) and the second fluid flowing through the second tube (43a) are formed. Prepared,
A space formed between adjacent tubes of the first tube (16a) and the second tube (43a) forms a third fluid passage (70a) through which the third fluid flows, and is used for the third fluid. In the passage (70a), heat exchange between the first fluid and the third fluid and heat exchange between the second fluid and the third fluid are promoted, and the first fluid and the second fluid flowing through the first tube (16a) are provided. Outer fins (50) that enable heat transfer between the second fluid flowing through the tube (43a) are arranged,
As the heat exchange section (71, 72), the upstream heat exchange section (71) disposed on the upstream side in the flow direction (X) of the third fluid and the downstream side in the flow direction (X) of the third fluid The downstream heat exchange section (72) is provided, and the first tube (16a) is disposed in both the upstream heat exchange section (71) and the downstream heat exchange section (72), and the second tube (43a ) Is disposed in at least one of the upstream heat exchange section (71) and the downstream heat exchange section (72), and the upstream heat exchange section (71) and the downstream heat exchange section (72) The part arrange | positioned so that 1st tube (16a) may superpose | polymerize when it sees from a flow direction (X), and the part arrange | positioned so that a 1st tube (16a) and a 2nd tube (43a) may superpose | polymerize Are arranged so that both exist,
The tank part (73) includes a plate header (731) to which the first and second tubes (16a, 43a) are joined, a tank header (732) that forms tank spaces (73a to 73c) therein, The intermediate plate (733) formed with a plurality of communication passages (733a, 733b) for communicating the two tubes (16a, 43a) and the tank spaces (73a-73c), and the communication passages (733a, 733b) and the tank space ( 73a to 73c) and a partition plate (734) in which a plurality of communication holes (734a to 734c) are formed.
Furthermore, in the tank part (73), three tank spaces (73a to 73c) arranged side by side in the flow direction (X) of the third fluid are formed, and the three tank spaces (73a to 73c) Of these, the central tank space (73c) is disposed at the center in the flow direction (X) of the third fluid, and the first and second tubes (16a, 43a) among the plurality of communication paths (733a, 733b). ) And the central tank space (73c) are connected to the central side communication path (733b), the central side communication path (733b) penetrates the front and back of the intermediate plate (733). It is formed by a through-hole, and when viewed from the longitudinal direction of the first and second tubes (16a, 43a), the central tank space from the position where it overlaps with the first and second tubes (16a, 43a). (73c) side It is characterized in heat exchanger formed in towards extending shape.

  According to this, the tank part (73) is comprised by the plate header (731), the tank header (732), the intermediate | middle plate (733), and the partition plate (734). Accordingly, the first fluid communication path and the second tube (43a) for communicating between the first tube (16a) formed in the tank portion (73) and the tank space (73a, 73b) for the first fluid. A communication path for the second fluid that communicates with the tank space (73c) for the second fluid can be formed by a through hole that penetrates the front and back of the intermediate plate (733).

  At this time, with respect to the upstream end tank space (73a) positioned on the most upstream side in the third fluid flow direction (X) among the three tank spaces (73a to 73c), the upstream heat exchange section (71) is provided. It is possible to easily communicate with the constituting tube.

  Similarly, with respect to the downstream end side tank space (73b) positioned on the most downstream side in the third fluid flow direction (X) among the three tank spaces (73a to 73c), the downstream heat exchange section (72) is provided. It is possible to easily communicate with the constituting tube.

  Further, with respect to the central tank space (73c), the first and second tubes (16a, 43a) constituting the upstream heat exchange section (71) and the first and second constituting the downstream heat exchange section (72). Even in any of the two tubes (16a, 43a), the center side communication path (733b) is easily formed by extending the center side from the first and second tubes (16a, 43a). Can be communicated to.

  Therefore, according to the present invention, in the heat exchanger configured to be able to exchange heat between the three types of fluids, the fluid flow path formed in the tank portion (73) can be easily formed. Can do. As a result, various path configurations can be easily realized, and the heat exchange performance of the entire heat exchanger can also be improved. Note that the path means a group of tubes in which the same kind of fluid distributed from the same distribution space flows in the same direction toward the same collective space.

  According to a second aspect of the present invention, in the heat exchanger according to the first aspect, the tank header (732) includes at least a central tank header (732a) forming a central tank space (73c), and a central tank. It has an end side tank header (732b) that forms tank spaces (73a, 73b) other than the space (73c), and an outer peripheral surface of the center side tank header (732a) and an outer peripheral surface of the end side tank header (732b). A space for heat insulation (73d) that suppresses heat transfer between the fluid in the center side tank header (732a) and the fluid in the end side tank header (732b) is formed therebetween.

  According to this, since the heat insulation space (73d) which suppresses the heat transfer between the fluid in the center side tank header (732a) and the fluid in the end side tank header (732b) is formed, three kinds of fluid In the heat exchanger configured to be able to exchange heat between them, unnecessary heat exchange between the fluids in the tank spaces (73a to 73c) can be suppressed.

  The unnecessary heat exchange between the fluids in the tank spaces (73a to 73c) includes not only unnecessary heat exchange between different kinds of fluids but also unnecessary heat exchange between the same kind of fluids.

  According to a third aspect of the present invention, in the heat exchanger according to the first or second aspect, the tank header (732) includes at least a central tank header (732a) that forms a central tank space (73c), and a central It has an end side tank header (732b) that forms tank spaces (73a, 73b) other than the side tank space (73c), and the center side tank header (732a) and the end side tank header (732b) are members different from each other. It is configured.

  According to this, since the center side tank header (732a) and the end side tank header (732b) are composed of different members, they are arranged in the tank portion (73) in the flow direction (X) of the third fluid. Insulating space that can easily form the three disposed tank spaces (73a to 73c) and suppresses heat transfer between the fluid in the central tank header (732a) and the fluid in the end tank header (732b). (73d) can be easily formed.

  Further, as in the invention according to claim 4, specifically, the heat exchanger according to any one of claims 1 to 3 is condensed by condensing the refrigerant in a vapor compression refrigeration cycle (10). Among the three tank spaces (73a to 73c), the one arranged on the most upstream side in the flow direction (X) of the third fluid is the upstream end side tank space (73a), and the third fluid space When the downstream end tank space (73b) is the one arranged on the most downstream side in the flow direction (X), the first fluid is a refrigerant of the refrigeration cycle (10), and the second fluid is an external heat source. The third fluid is outdoor air, the central tank space (73c) forms a space for collecting or distributing the heat medium, and the upstream end tank space ( 73a) and less of the downstream end side tank space (73b) Also one may form a most downstream side refrigerant collection space to set the refrigerant to flow out to the outside.

  According to this, in the heat exchanger configured to be able to exchange heat between the three types of fluids of the refrigerant, the heat medium, and the outdoor air in the refrigeration cycle, between the refrigerant and the heat medium in the tank unit (73). Unnecessary heat exchange can be suppressed. Therefore, deterioration of the coefficient of performance of the refrigeration cycle (10) can be suppressed.

  In addition, the code | symbol in the bracket | parenthesis of each means described in this column and the claim shows the correspondence with the specific means as described in embodiment mentioned later.

It is a whole block diagram which shows the refrigerant | coolant flow path etc. at the time of the heating operation of the heat pump cycle of 1st Embodiment. It is a whole block diagram which shows the refrigerant | coolant flow path etc. at the time of the defrost operation of the heat pump cycle of 1st Embodiment. It is a whole block diagram which shows the refrigerant | coolant flow path etc. at the time of the air_conditionaing | cooling operation of the heat pump cycle of 1st Embodiment. It is an external appearance perspective view of the heat exchanger of 1st Embodiment. It is VV sectional drawing of FIG. It is a disassembled perspective view of the heat exchanger of 1st Embodiment. It is VII-VII sectional drawing of FIG. It is VIII-VIII sectional drawing of FIG. It is a typical perspective view explaining the flow of the refrigerant and cooling water in the heat exchanger of a 1st embodiment. It is sectional drawing of the heat exchanger of 2nd Embodiment. It is sectional drawing of the heat exchanger of the modification of 2nd Embodiment. It is sectional drawing of the heat exchanger of 3rd Embodiment. It is sectional drawing of the heat exchanger of the modification of 3rd Embodiment. It is a typical perspective view explaining the flow of the refrigerant | coolant and cooling water in the heat exchanger of 4th Embodiment. It is a whole block diagram which shows the refrigerant | coolant flow path etc. at the time of the waste heat recovery driving | operation in 5th Embodiment.

(First embodiment)
A first embodiment of the present invention will be described with reference to FIGS. As shown in FIGS. 1 to 3, the composite heat exchanger 70 of the present embodiment includes a heat pump cycle 10 (vapor compression refrigeration) that adjusts the temperature of blown air that is blown into the vehicle interior in the vehicle air conditioner 1. Cycle). Furthermore, the vehicle air conditioner 1 of the present embodiment is applied to a so-called hybrid vehicle that obtains a driving force for vehicle traveling from an internal combustion engine (engine) and a traveling electric motor MG.

  The hybrid vehicle operates or stops the engine in accordance with the traveling load of the vehicle, etc., obtains driving force from both the engine and the traveling electric motor MG, or travels when the engine is stopped. It is possible to switch the running state where the driving force is obtained only from the MG. Thereby, in a hybrid vehicle, vehicle fuel consumption can be improved compared to a normal vehicle that obtains driving force for vehicle travel only from the engine.

  The heat pump cycle 10 is a vapor compression refrigeration cycle that functions in the vehicle air conditioner 1 to heat or cool the blown air that is blown into the vehicle interior that is the air-conditioning target space. Therefore, the heat pump cycle 10 switches the refrigerant flow path, heats the blown air that is the heat exchange target fluid to heat the vehicle interior, and heats the vehicle interior, and cools the blown air to cool the vehicle interior. Cooling operation (cooling operation) can be executed.

  Further, in the heat pump cycle 10, a defrosting operation is performed to melt and remove frost attached to the outdoor heat exchange unit 16 of the composite heat exchanger 70 described later that functions as an evaporator that evaporates the refrigerant during the heating operation. You can also. In addition, in the whole block diagram shown to the heat pump cycle 10 of FIGS. 1-3, the flow of the refrigerant | coolant at the time of heating operation, a defrost operation, and also the air_conditionaing | cooling operation is shown by the solid line arrow, respectively.

  In the heat pump cycle 10 of the present embodiment, an HFC refrigerant (specifically, R134a) is adopted as the refrigerant, and a subcritical refrigeration cycle in which the high-pressure side refrigerant pressure does not exceed the refrigerant critical pressure is configured. Yes. Of course, an HFO refrigerant (specifically, R1234yf) or the like may be adopted as the refrigerant. Furthermore, refrigeration oil for lubricating the compressor 11 is mixed in the refrigerant, and a part of the refrigeration oil circulates in the cycle together with the refrigerant.

  Among the components of the heat pump cycle 10, the compressor 11 is disposed in the engine room, sucks in refrigerant, compresses and discharges it, and uses a fixed displacement compressor 11 a with a fixed discharge capacity as an electric motor. It is comprised as an electric compressor driven by 11b. Specifically, various compression mechanisms such as a scroll compression mechanism and a vane compression mechanism can be employed as the fixed capacity compressor 11a.

  The operation (rotation speed) of the electric motor 11b is controlled by a control signal output from an air conditioning control device to be described later, and either an AC motor or a DC motor may be adopted. And the refrigerant | coolant discharge capability of the compressor 11 is changed by rotation speed control of this electric motor 11b. Therefore, in the present embodiment, the electric motor 11b constitutes the discharge capacity changing means of the compressor 11.

  The refrigerant outlet side of the compressor 11 is connected to the refrigerant inlet side of the indoor condenser 12. The indoor condenser 12 is disposed in the casing 31 of the indoor air conditioning unit 30 of the vehicle air conditioner 1, and exchanges heat between the high-temperature and high-pressure refrigerant flowing through the interior of the indoor condenser 12 and the blown air after passing through the indoor evaporator 20 described later. It is a heat exchanger for heating. The detailed configuration of the indoor air conditioning unit 30 will be described later.

  Connected to the refrigerant outlet side of the indoor condenser 12 is a heating fixed throttle 13 as a decompression means for heating operation for decompressing and expanding the refrigerant flowing out of the indoor condenser 12 during the heating operation. As the heating fixed throttle 13, an orifice, a capillary tube or the like can be adopted. The refrigerant inlet side of the outdoor heat exchanger 16 of the composite heat exchanger 70 is connected to the outlet side of the heating fixed throttle 13.

  Furthermore, a fixed throttle bypass passage 14 is connected to the refrigerant outlet side of the indoor condenser 12 to guide the refrigerant flowing out of the indoor condenser 12 to the outdoor heat exchanger 16 side by bypassing the heating fixed throttle 13. Yes. The fixed throttle bypass passage 14 is provided with an on-off valve 15a for opening and closing the fixed throttle bypass passage 14. The on-off valve 15a is an electromagnetic valve whose opening / closing operation is controlled by a control voltage output from the air conditioning control device.

  Further, the pressure loss that occurs when the refrigerant passes through the on-off valve 15 a is extremely small compared to the pressure loss that occurs when the refrigerant passes through the fixed throttle 13. Accordingly, the refrigerant that has flowed out of the indoor condenser 12 flows into the outdoor heat exchanger 16 via the fixed throttle bypass passage 14 when the on-off valve 15a is open, and when the on-off valve 15a is closed. Flows into the outdoor heat exchanger 16 through the heating fixed throttle 13.

  Thereby, the on-off valve 15 a can switch the refrigerant flow path of the heat pump cycle 10. Accordingly, the on-off valve 15a of the present embodiment functions as a refrigerant flow path switching unit. Such refrigerant flow switching means includes a refrigerant circuit connecting the outlet side of the indoor condenser 12 and the inlet side of the fixed throttle 13 for heating, the outlet side of the indoor condenser 12 and the inlet side of the fixed throttle bypass passage 14. An electric three-way valve or the like that switches the refrigerant circuit that connects the two may be employed.

  The outdoor heat exchange unit 16 is a heat exchange unit that exchanges heat between the refrigerant circulating in the heat exchanger 70 and the outside air (outdoor air) blown from the blower fan 17. This outdoor heat exchange unit 16 is disposed in the engine room and functions as an evaporating heat exchange unit that evaporates the low-pressure refrigerant and exerts an endothermic effect during heating operation, and dissipates heat to dissipate the high-pressure refrigerant during cooling operation. Functions as a heat exchanger.

  The blower fan 17 is an electric blower in which the operation rate, that is, the rotation speed (the amount of blown air) is controlled by a control voltage output from the air conditioning control device. Furthermore, in the heat exchanger 70 of the present embodiment, the outdoor heat exchange unit 16 described above, and the radiator unit 43 that performs heat exchange between the cooling water that cools the traveling electric motor MG and the outside air that is blown from the blower fan 17. It is composed integrally.

  For this reason, the blower fan 17 of the present embodiment constitutes an outdoor blower that blows outside air toward both the outdoor heat exchange unit 16 and the radiator unit 43. The detailed configuration of the composite heat exchanger 70 in which the outdoor heat exchanger 16 and the radiator 43 are integrally configured will be described later.

  An electrical three-way valve 15 b is connected to the outlet side of the outdoor heat exchanger 16 of the heat exchanger 70. The operation of the three-way valve 15b is controlled by a control voltage output from the air conditioning control device, and constitutes a refrigerant flow switching means together with the above-described on-off valve 15a.

  Specifically, the three-way valve 15b switches to a refrigerant flow path that connects an outlet side of the outdoor heat exchange unit 16 and an inlet side of an accumulator 18 described later during heating operation, and the outdoor heat exchange unit 16 during cooling operation. Is switched to the refrigerant flow path connecting the outlet side of the cooling air and the inlet side of the cooling expansion valve 19.

  The cooling expansion valve 19 is a pressure reducing means for cooling operation that decompresses and expands the refrigerant that has flowed out of the outdoor heat exchanger 16 during the cooling operation. More specifically, the cooling expansion valve 19 includes a valve body configured to be able to change the throttle opening (refrigerant passage area), and an electric actuator including a stepping motor that changes the throttle opening of the valve body. This is an electric variable aperture mechanism that is configured to include: The operation of the cooling expansion valve 19 is controlled by a control signal output from the air conditioning control device.

  The refrigerant inlet side of the indoor evaporator 20 is connected to the outlet side of the cooling expansion valve 19. The indoor evaporator 20 is disposed in the casing 31 of the indoor air-conditioning unit 30 on the upstream side of the air flow with respect to the indoor condenser 12, and exchanges heat between the refrigerant circulating in the interior and the blown air, thereby blowing air. It is a heat exchanger for cooling which cools. The inlet side of the accumulator 18 is connected to the refrigerant outlet side of the indoor evaporator 20.

  The accumulator 18 is a gas-liquid separator for a low-pressure side refrigerant that separates the gas-liquid refrigerant flowing into the accumulator 18 and stores excess refrigerant in the cycle. The suction side of the compressor 11 is connected to the gas-phase refrigerant outlet of the accumulator 18. Accordingly, the accumulator 18 functions to prevent the compressor 11 from being compressed by suppressing the suction of the liquid phase refrigerant into the compressor 11.

  Next, the indoor air conditioning unit 30 will be described. The indoor air-conditioning unit 30 is disposed inside the instrument panel (instrument panel) at the foremost part of the vehicle interior, and a blower 32, the above-described indoor condenser 12, the indoor evaporator 20 and the like are provided in a casing 31 that forms the outer shell thereof. Is housed.

  The casing 31 forms an air passage for blown air that is blown into the vehicle interior, and is formed of a resin (for example, polypropylene) that has a certain degree of elasticity and is excellent in strength. An inside / outside air switching device 33 for switching and introducing vehicle interior air (inside air) and outside air is arranged on the most upstream side of the blown air flow in the casing 31.

  The inside / outside air switching device 33 is formed with an inside air introduction port for introducing inside air into the casing 31 and an outside air introduction port for introducing outside air. Furthermore, inside / outside air switching device 33 is provided with an inside / outside air switching door that continuously adjusts the opening area of the inside air introduction port and the outside air introduction port to change the air volume ratio between the inside air volume and the outside air volume. Has been.

  On the downstream side of the air flow of the inside / outside air switching device 33, a blower 32 that blows air sucked through the inside / outside air switching device 33 toward the vehicle interior is arranged. The blower 32 is an electric blower that drives a centrifugal multiblade fan (sirocco fan) with an electric motor, and the number of rotations (the amount of blown air) is controlled by a control voltage output from the air conditioning control device.

  On the downstream side of the air flow of the blower 32, the indoor evaporator 20 and the indoor condenser 12 are arranged in this order with respect to the flow of the blown air. In other words, the indoor evaporator 20 is disposed upstream of the indoor condenser 12 in the flow direction of the blown air.

  Further, on the downstream side of the air flow of the indoor evaporator 20 and the upstream side of the air flow of the indoor condenser 12, the ratio of the amount of air passing through the indoor condenser 12 in the blown air after passing through the indoor evaporator 20. An air mix door 34 for adjusting the air pressure is disposed. Further, on the downstream side of the air flow of the indoor condenser 12, the blown air heated by exchanging heat with the refrigerant in the indoor condenser 12 and the blown air that is not heated bypassing the indoor condenser 12 are mixed. A mixing space 35 is provided.

  An air outlet that blows the conditioned air mixed in the mixing space 35 into the passenger compartment, which is a space to be cooled, is disposed at the most downstream portion of the air flow of the casing 31. Specifically, as this air outlet, a face air outlet that blows air-conditioned air toward the upper body of the passenger in the passenger compartment, a foot air outlet that blows air-conditioned air toward the feet of the passenger, and the inner surface of the front window glass of the vehicle A defroster outlet (both not shown) is provided to blow air-conditioned air toward the front.

  Therefore, the temperature of the conditioned air mixed in the mixing space 35 is adjusted by adjusting the ratio of the air volume that the air mix door 34 passes through the indoor condenser 12, and the temperature of the conditioned air blown out from each outlet is adjusted. Is adjusted. That is, the air mix door 34 constitutes a temperature adjusting means for adjusting the temperature of the conditioned air blown into the vehicle interior.

  In other words, the air mix door 34 functions as heat exchange amount adjusting means for adjusting the heat exchange amount between the refrigerant discharged from the compressor 11 and the blown air in the indoor condenser 12. The air mix door 34 is driven by a servo motor (not shown) whose operation is controlled by a control signal output from the air conditioning control device.

  Further, on the upstream side of the air flow of the face outlet, the foot outlet, and the defroster outlet, a face door for adjusting the opening area of the face outlet, a foot door for adjusting the opening area of the foot outlet, and the defroster outlet, respectively. A defroster door (none of which is shown) for adjusting the opening area is arranged.

  These face doors, foot doors, and defroster doors constitute the outlet mode switching means for switching the outlet mode, and their operation is controlled by a control signal output from the air conditioning controller via a link mechanism or the like. Driven by a servo motor (not shown).

  Next, the cooling water circulation circuit 40 will be described. This cooling water circulation circuit 40 has cooling water (cooling medium) as a cooling medium (heating medium) in a cooling water passage formed inside a traveling electric motor MG (external heat source) which is one of in-vehicle devices that generate heat during operation. For example, it is a cooling water circulation circuit that circulates an ethylene glycol aqueous solution) and cools the traveling electric motor MG.

  The cooling water circulation circuit 40 includes a cooling water pump 41, an electric three-way valve 42, a radiator portion 43 of a composite heat exchanger 70, a bypass passage 44 for bypassing the radiator portion 43 and flowing cooling water. Has been.

  The cooling water pump 41 is an electric pump that pumps the cooling water in the cooling water circulation circuit 40 to a cooling water passage formed inside the traveling electric motor MG, and the number of rotations is controlled by a control signal output from the air conditioning control device. (Flow rate) is controlled. Therefore, the cooling water pump 41 functions as a cooling capacity adjusting unit that adjusts the cooling capacity by changing the flow rate of the cooling water that cools the traveling electric motor MG.

  The three-way valve 42 is connected to the inlet side of the cooling water pump 41 and the outlet side of the radiator section 43 so that the cooling water flows into the radiator section 43, and the inlet side of the cooling water pump 41 and the bypass passage 44 is a cooling water circuit switching unit that connects the outlet side of 44 and switches the cooling water circuit that flows the cooling water around the radiator unit 43. Further, the operation of the three-way valve 42 is controlled by a control voltage output from the air conditioning control device.

  That is, in the cooling water circulation circuit 40 of this embodiment, as shown by the broken line arrow in FIG. Switching between the circuit and the cooling water circuit that circulates the cooling water in the order of the cooling water pump 41 → the traveling electric motor MG → the radiator 43 → the cooling water pump 41 as shown by the broken line arrows in FIGS. it can.

  Therefore, when the three-way valve 42 is switched to a cooling water circuit that flows the cooling water around the radiator 43 while the electric motor MG for traveling is in operation, the cooling water does not radiate heat at the radiator 43 and the temperature To raise. That is, when the three-way valve 42 is switched to the cooling water circuit that flows the cooling water by bypassing the radiator 43, the heat amount (heat generation amount) of the traveling electric motor MG is stored in the cooling water. .

  On the other hand, when the three-way valve 42 switches to the cooling medium circuit that flows the cooling water so as to flow through the radiator 43 during the operation of the electric motor MG for traveling, the cooling water flows into the radiator 43 and is sent from the blower fan 17. Exchanges heat with the blown outside air. Furthermore, in the heat exchanger 70 of the present embodiment, the cooling water that has flowed into the radiator section 43 can exchange heat not only with the outside air but also with the refrigerant that flows through the outdoor heat exchange section 16.

  Next, a detailed configuration of the composite heat exchanger 70 of the present embodiment will be described with reference to FIGS. In addition, the up and down arrows in FIG. 4 indicate the up and down directions when the composite heat exchanger 70 is mounted in the casing 31 of the indoor air conditioning unit 30.

  First, as shown in the external perspective view of FIG. 4, the heat exchanger 70 includes a plurality of tubes through which refrigerant or cooling water flows, and refrigerants that are arranged on both ends of the plurality of tubes and flow through the tubes. Or it is comprised in what is called a tank and tube type heat exchanger structure comprised including a pair of tank part 73 etc. in which the tank space which collects or distributes cooling water was formed.

  Specifically, the heat exchanger 70 includes a plurality of refrigerant tubes 16a (first tubes) in which a refrigerant that is a first fluid flows, and a plurality of cooling in which cooling water that is a second fluid flows. It has a water tube 43a (second tube). Further, in the heat exchanger 70, the refrigerant tubes 16a and the cooling water tubes 43a are stacked, so that a heat exchanging unit that exchanges heat between the refrigerant and the outside air and exchanges heat between the cooling water and the outside air is provided. It is configured.

  In this heat exchange section, as shown in the cross-sectional view of FIG. 5, two rows of arrays in which the refrigerant tubes 16a and the cooling water tubes 43a are stacked are provided in the flow direction X of the outside air that is the third fluid. . Therefore, in the heat exchanging unit 70 of the present embodiment, as the heat exchanging unit, the upstream heat exchanging unit 71 disposed on the upstream side in the outside air flow direction X and the downstream disposed on the downstream side in the outside air flowing direction X. A side heat exchange unit 72 is provided.

  In addition, as shown in FIG. 5, in the present embodiment, a tube having a flat multi-hole cross section formed by extrusion is employed as the refrigerant tube 16a, and as the cooling water tube 43a, 1 A tube having a flat two-hole cross-sectional shape formed by bending a sheet of plate material is employed.

  Further, the upstream heat exchanging unit 71 is configured by alternately stacking the refrigerant tubes 16a and the cooling water tubes 43a one by one. More specifically, the refrigerant tube 16a and the cooling water tube 43a constituting the upstream heat exchange section 71 are spaced apart from each other so that the flat surfaces of the outer surfaces are parallel to each other and face each other. Are alternately stacked.

  Therefore, in the upstream heat exchange section 71, heat can be exchanged between the refrigerant flowing through the refrigerant tube 16a and the outside air flowing around the refrigerant tube 16a, and the cooling water flowing through the cooling water tube 43a Heat exchange can be performed with the outside air flowing around the cooling water tube 43a.

  The downstream heat exchange section 72 is configured by stacking the refrigerant tubes 16a. More specifically, the refrigerant tubes 16a constituting the downstream heat exchange section 72 are also laminated and arranged at predetermined intervals so that the flat surfaces of the outer surfaces are parallel to each other and face each other. Yes. Therefore, in the downstream heat exchange section 72, heat exchange can be performed between the refrigerant flowing through the refrigerant tube 16a and the outside air flowing around the refrigerant tube 16a.

  Further, the tubes 16a and 43a constituting the upstream heat exchange section 71 and the tubes 16a constituting the downstream heat exchange section 72 are arranged so as to overlap each other when viewed from the flow direction X of the outside air. ing.

  Here, in the present embodiment, the ratio of the number of the refrigerant tubes 16a to the total number of tubes constituting the upstream heat exchange section 71 and the refrigerant tubes relative to the total number of tubes constituting the downstream heat exchange section 72 are described. Since the number ratio of 16a is different, the refrigerant tubes 16a are arranged in the upstream heat exchanging portion 71 and the downstream heat exchanging portion 72 so that the refrigerant tubes 16a are superposed when viewed from the flow direction X of the outside air. There will be a part and a part where the refrigerant tube 16a and the cooling water tube 43a are superposed.

  In addition, a space formed between the refrigerant tube 16a and the cooling water tube 43a constituting the upstream heat exchange section 71 and a space between the adjacent refrigerant tubes 16a constituting the downstream heat exchange section 72 are formed. This space forms an outside air passage 70a (third fluid passage) through which the outside air blown by the blower fan 17 circulates.

  In the outside air passage 70a, heat exchange between the refrigerant and the outside air and heat exchange between the cooling water and the outside air are promoted, and the refrigerant and the cooling water flowing through the refrigerant tube 16a constituting the upstream heat exchanging portion 71 are promoted. The outer fins 50 are arranged to enable heat transfer between the coolant flowing through the tubes 43a and the heat transfer between the refrigerants flowing through the adjacent refrigerant tubes 16a constituting the downstream heat exchange section 72. Yes.

  As this outer fin 50, the corrugated fin which bent and formed the metal thin plate excellent in heat conductivity into the wave shape is employable. More specifically, in the present embodiment, the outer fin 50 is joined to both the refrigerant tube 16a and the cooling water tube 43a constituting the upstream heat exchanging portion 71, thereby cooling the refrigerant tube 16a and the cooling tube. Heat transfer between the water tube 43a is possible.

  Next, the tank unit 73 will be described. As shown in FIGS. 6 to 8, three tank spaces 73 a to 73 c arranged side by side in the outside air flow direction X are formed inside the tank portion 73 of the present embodiment. These tank spaces 73a to 73c are all formed in a shape extending in the stacking direction of the refrigerant tube 16a and the cooling water tube 43a.

  In the following description, among the three tank spaces 73a to 73c arranged side by side in the outside air flow direction X, the one arranged on the most upstream side in the outside air flow direction X is referred to as the upstream end side tank space 73a. The downstream end tank space 73b is arranged at the most downstream side in the outside air flow direction X, and further, the center of the outside air flow direction X, that is, the upstream end tank space 73a and the downstream end tank space 73b. The one disposed between them is referred to as a central tank space 73c.

  As shown in the exploded perspective view of FIG. 6, the tank portion 73 includes a plate header 731 to which the refrigerant tube 16a and the cooling water tube 43a are joined, a tank header 732 that forms tank spaces 73a to 73c therein, and The refrigerant tube 16a, the cooling water tube 43a, and the tank spaces 73a to 73c are communicated with each other, and a plurality of communication paths (fluid flow paths) 733a and 733b are formed, and an intermediate plate 733 and a partition plate 734 are formed. ing.

  The intermediate plate 733 is formed of a plate-like member provided with a plurality of through holes penetrating the front and back surfaces. These through holes have a plurality of refrigerants communicating with the refrigerant tube 16a by joining one plate surface of the intermediate plate 733 to the inner surface of the plate header 731 and bonding the other plate surface to the partition plate 734. A plurality of cooling water communication paths 733b communicating with the communication communication path 733a and the cooling water tube 43a are formed.

  Furthermore, these through holes are provided at positions where they overlap with the open ends of the tubes 16a and 43a communicating with each other when viewed from the longitudinal direction of the refrigerant tube 16a and the cooling water tube 43a. Accordingly, the through holes are also provided in two rows in the flow direction X of the outside air so as to correspond to the tubes 16a and 43a constituting the upstream heat exchange section 71 and the tubes 16a constituting the downstream heat exchange section 72. Yes.

  Further, if the communication passage communicating with the central tank space 73c among the refrigerant communication passage 733a and the cooling water communication passage 733b formed by the through holes is a central communication passage, the central communication passage is the refrigerant tube 16a. Further, when viewed from the longitudinal direction of the cooling water tube 43a, the cooling water tube 43a is formed in a shape extending toward the central tank space 73c from a position where it overlaps with the open end of the communicating tube. In other words, the center side communication path is formed longer in the flow direction X of the outside air than the other communication paths.

  The partition plate 734 is a plate-like member joined to the surface of the intermediate plate 733 on the tank space 73a to 73c side, and includes the refrigerant communication passage 733a, the coolant communication passage 733b, and the tank spaces 73a. A plurality of first to third communication holes 734a to 734c that communicate with ˜73c are formed.

  As shown in FIGS. 7 and 8, depending on the positions of the first to third communication holes 734a to 734c, the refrigerant tube 16a and the cooling water tube 43a are respectively connected to the refrigerant communication passage 733a and the cooling water communication. The tank spaces 73a to 73c communicating with each other through the passage 733b are determined.

  Specifically, in the heat exchanger 70 of the present embodiment, the refrigerant tube 16a constituting the upstream heat exchange unit 71 includes the refrigerant communication passage 733a and the first refrigerant passage 733a arranged on the upstream side in the flow direction X of the outside air. It communicates with the upstream end side tank space 73a through the communication hole 734a. Further, the cooling water tube 43a constituting the downstream heat exchange section 72 is connected to the downstream end tank space via the refrigerant communication passage 733a and the third communication hole 734c arranged on the upstream side in the flow direction X of the outside air. 73b.

  Further, the cooling water tube 43a constituting the upstream heat exchange section 71 communicates with the central tank space 73c via the cooling water communication passage 733b and the second communication hole 734b. Therefore, in the present embodiment, the cooling water communication path 733b constitutes the central communication path.

  Next, the tank header 732 is formed by combining a plurality of members. Specifically, the tank header 732 includes a central tank header 732a that forms the central tank space 73c, and tank spaces other than the central tank space 73c (that is, the upstream end tank space 73a and the downstream end tank space). 73b) is combined with the end side tank header 732b.

  The center side tank header 732a has a first member 732c formed in a U-shaped cross section when viewed from the longitudinal direction, and a second member formed in an arc shape in cross section when viewed from the longitudinal direction. It is formed in a cylindrical shape by combining with 732d. On the other hand, the end-side tank header 732b is formed in a two-sided cross section when viewed from the longitudinal direction, and the center-side tank header 732a is disposed in the central valley (recess).

  Further, when viewed from the longitudinal direction of the tank portion 73, the outer peripheral surface of the center side tank header 732a and the outer peripheral surface of the end side tank header 732b are in close contact with each other as shown in FIGS. The gap is formed without any problems. This gap forms a heat insulating space 73d that suppresses heat transfer between the fluid in the central tank header 732a (cooling water in the present embodiment) and the fluid in the end tank header 732b (refrigerant in the present embodiment). Forming.

  6 to 8 show an exploded perspective view of a part of the upper tank portion 73 in FIG. 4, the basic structure of the lower tank portion 73 is also the upper tank. This is the same as the unit 73. Further, the lower tank portion 73 is provided with a communication passage formed in the intermediate plate 733 that allows the upstream end side tank space 73a and the downstream end side tank space 73b to communicate with each other.

  Further, a separator (not shown) that divides the upstream end side tank space 73a in the longitudinal direction is disposed in the upstream end side tank space 73a of the upper and lower tank portions 73. As shown in FIGS. 4 and 9, a refrigerant inflow port 161 for allowing the refrigerant to flow into one upstream end side tank space 73 a divided by the separator is provided at one end in the longitudinal direction of the upper tank portion 73. Provided at the other end in the longitudinal direction is a refrigerant outflow port 162 through which refrigerant flows out from the other upstream end side tank space 73a divided by the separator.

  Similarly, a separator (not shown) that divides the central tank space 73c in the longitudinal direction is disposed in the central tank space 73c of the upper tank portion 73. As shown in FIG. 4, a cooling water inflow port 431 for allowing the refrigerant to flow into one space divided by the separator is provided on one end side in the longitudinal direction of the tank portion 73, and on the other end side in the longitudinal direction. A cooling water outflow port 432 is provided for allowing the refrigerant to flow out from the other space divided by the separator.

  And in the heat exchanger 70 of this embodiment, as shown by the thick solid line arrow of FIG. 9, the refrigerant | coolant which flowed into the upstream end side tank space 73a of the upper tank part 73 from the refrigerant | coolant inflow port 161 is upstream heat | fever. The refrigerant is distributed to the refrigerant tube 16a group on a part of the exchange unit 71 (on the right side in FIG. 9, that is, the refrigerant inflow port 161 and the cooling water inflow port 431 side) to the upstream end side tank space 73a of the tank unit 73 on the lower side. Gather.

  The refrigerant that has gathered into the upstream end side tank space 73a of the lower side tank part 73 passes through the communication path formed in the intermediate plate of the lower side tank part 73, and the downstream end side tank space of the lower side tank part 73. It flows into 73b.

  Furthermore, the refrigerant that has flowed into the downstream end side tank space 73b of the lower side tank unit 73 is distributed to a part of the downstream side heat exchange unit 72 (on the right side in FIG. 9) refrigerant tube 16a group, and the upper side side. The tank portion 73 gathers in the downstream end side tank space 73b.

  The refrigerant that has gathered into the downstream end side tank space 73b of the upper tank portion 73 flows from the right side to the left side in FIG. 9, and the remainder of the downstream heat exchange unit 72 (on the left side in FIG. 9, ie, the refrigerant outflow port 162 and It is distributed to the refrigerant tube 16a group on the cooling water outflow port 432 side, and gathers in the downstream end side tank space 73b of the lower tank portion 73.

  The refrigerant gathered in the downstream end side tank space 73b of the lower side tank part 73 passes through the communication path formed in the intermediate plate 733 of the lower side tank part 73 and the upstream end side tank of the lower side tank part 73. It flows into the space 73a.

  The refrigerant that has flowed into the upstream end tank space 73a of the lower tank section 73 is distributed to the remaining refrigerant tube 16a group (left side in FIG. 9) of the downstream heat exchange section 72, and the upper tank section 73 is distributed. To the upstream end side tank space 73a. The refrigerant gathered in the upstream end side tank space 73 a of the upper tank portion 73 flows out from the refrigerant outflow port 162.

  In other words, in the heat exchanger 70 of the present embodiment, as a path configuration through which the refrigerant flows, the refrigerant distributed from the right side of the upstream end side tank space 73a of the upper tank part 73 is upstream of the lower tank part 73. The first path 16P1 that collects to the right side of the end side tank space 73a, the refrigerant distributed from the right side of the downstream end side tank space 73b of the lower side tank unit 73, and the downstream end side tank space 73b of the upper side tank unit 73. A second path 16P2 that collects to the right side, and a third refrigerant that collects refrigerant distributed from the left side of the downstream end side tank space 73b of the upper side tank unit 73 to the left side of the downstream end side tank space 73b of the lower side tank unit 73. The refrigerant distributed from the left side of the upstream end tank space 73a of the path 16P3 and the lower tank portion 73 is moved to the left side of the upstream end tank space 73a of the upper tank portion 73. The third path 16P4 is formed engaged.

  Note that the path means a group of tubes in which the same kind of fluid distributed from the same distribution space flows in the same direction toward the same collective space.

  Furthermore, in the present embodiment, the space on the left side of the upstream end tank space 73a of the upper tank portion 73 (the space communicating with the refrigerant outflow port 162) collects the refrigerant that flows out of the heat exchanger 70. A downstream refrigerant collecting space is formed.

  Further, when viewed from the flow direction of the outside air, the downstream end side tank of the upper side tank unit 73 that distributes the refrigerant to the space arranged to overlap with the most downstream side refrigerant collecting space, that is, the third path 16P3. The space on the left side of the space 73b exchanges heat with the outside air when passing through the first and second paths, so that the temperature difference with the refrigerant in the most downstream side refrigerant assembly space rather than the refrigerant immediately after flowing in from the outside. An intermediate temperature refrigerant space into which a small amount of refrigerant flows is formed.

  On the other hand, with respect to the cooling water, as indicated by the thick broken line arrows in FIG. 9, the cooling water flowing into the central tank space 73 c of the upper tank portion 73 from the cooling water inflow port 431 passes through the upstream heat exchange portion 71. The water is distributed to a part (right side in FIG. 9) of the cooling water tube 43 a and gathers in the central tank space 73 c of the tank part 73 on the lower side.

  The cooling water gathered in the central tank space 73c of the tank part 73 on the lower side flows from the right side to the left side in FIG. 9, and to the remaining cooling water tube 43a of the upstream heat exchange part 71 (left side in FIG. 9). It is distributed and gathers in the central tank space 73c of the upper tank portion 73. The cooling water gathered in the central tank space 73 c of the upper tank portion 73 flows out from the cooling water outflow port 432.

  In other words, in the heat exchanger 70 of the present embodiment, as a path configuration through which cooling water flows, the refrigerant distributed from the right side of the central tank space 73c of the upper tank portion 73 is transferred to the center of the lower tank portion 73. The first path 43P1 that collects to the right side of the side tank space 73c, and the refrigerant distributed from the left side of the center side tank space 73c of the lower tank part 73 to the left side of the center side tank space 73c of the upper side tank part 73 A second path 43P2 to be assembled is formed.

  Further, in the present embodiment, the space on the left side of the central tank space 73c of the upper tank portion 73 (the space communicating with the cooling water outflow port 432) collects the cooling water that flows out of the heat exchanger 70. The most downstream heat medium assembly space is formed. Further, when viewed from the flow direction X of the outside air, the most downstream heat medium assembly space and the most downstream refrigerant assembly space are arranged to be superposed.

  7 and FIG. 8, the thick solid line arrows and the thick broken line arrows indicate the tanks constituting the left area of FIG. 9 (that is, the area on the refrigerant outflow port 162 and cooling water outflow port 432 side). The flow of the refrigerant and cooling water in the section of part 73 is shown.

  As described above, in the heat exchanger 70 of the present embodiment, the outdoor heat exchange unit 16 is configured by both the refrigerant tube 16a of the upstream heat exchange unit 71 and the refrigerant tube 16a of the downstream heat exchange unit 72. The radiator section 43 is constituted by the cooling water tube 43a of the upstream heat exchange section 71.

  In addition, the refrigerant tubes 16a, the cooling water tubes 43a, the tank 73 and the outer fins 50 of the heat exchanger 70 described above are all formed of the same metal material (in this embodiment, an aluminum alloy). Has been. And the outdoor heat exchange part 16 and the radiator part 43 are integrated by brazing these components.

  Next, the electric control unit of this embodiment will be described. The air conditioning control device is composed of a well-known microcomputer including a CPU, ROM, RAM, etc. and its peripheral circuits, performs various calculations and processing based on an air conditioning control program stored in the ROM, and is connected to the output side. The various air conditioning control devices 11, 15a, 15b, 17, 19, 41, 42 and the like are controlled.

  Further, on the input side of the air conditioning control device, an inside air sensor that detects the temperature inside the vehicle, an outside air sensor that detects outside air temperature, a solar radiation sensor that detects the amount of solar radiation in the vehicle interior, and the temperature of the air blown from the indoor evaporator 20 (evaporator) An evaporator temperature sensor for detecting the temperature), a discharge refrigerant temperature sensor for detecting the refrigerant discharge refrigerant temperature, a discharge refrigerant pressure sensor for detecting the compressor 11 discharge refrigerant pressure, and an outdoor heat exchanger 16 outlet side refrigerant temperature Te. Outlet refrigerant temperature sensor, outdoor heat exchanger 16 outlet refrigerant pressure sensor for detecting the outlet side refrigerant pressure, cooling water temperature sensor for detecting the cooling water temperature Tw flowing into the traveling electric motor MG, etc. Sensor groups are connected.

  Further, an operation panel (not shown) disposed near the instrument panel in front of the passenger compartment is connected to the input side of the air conditioning control device, and operation signals from various air conditioning operation switches provided on the operation panel are input. . As various air conditioning operation switches provided on the operation panel, there are provided an operation switch of a vehicle air conditioner, a vehicle interior temperature setting switch for setting the vehicle interior temperature, an operation mode selection switch, and the like.

  In the air conditioning control device of this embodiment, control means for controlling the operation of various control target devices connected to the output side is integrally configured, but controls the operation of each control target device. The configuration (hardware and software) constitutes control means for controlling the operation of each control target device.

  For example, in the air-conditioning control device, the configuration for controlling the operation (refrigerant discharge capacity) of the compressor 11 constitutes the compressor control means, and the configuration for controlling the operations of the various devices 15a and 15b constituting the refrigerant flow path switching means. Constitutes the refrigerant flow path control means, and the construction for controlling the operation of the three-way valve 42 constituting the cooling water circuit switching means constitutes the cooling water circuit control means. Of course, the compressor control means, the refrigerant circuit control means, and the like may be configured separately from the air conditioning control device.

  Further, the air conditioning control device of the present embodiment is configured to determine whether or not frost formation has occurred in the outdoor heat exchange unit 16 based on the detection signal of the above-described air conditioning control sensor group (frosting determination unit). have. Specifically, in the frost determination unit of the present embodiment, the vehicle speed of the vehicle is a predetermined reference vehicle speed (20 km / h in the present embodiment) or less, and the outdoor heat exchanger 16 outlet side refrigerant temperature is When Te is 0 ° C. or lower, it is determined that frost formation has occurred in the outdoor heat exchanger 16.

  Next, the operation of the vehicle air conditioner 1 of the present embodiment having the above configuration will be described. In the vehicle air conditioner 1 of the present embodiment, a heating operation for heating the vehicle interior and a cooling operation for cooling the vehicle interior can be performed, and a defrosting operation can be performed during the heating operation. The operation in each operation will be described below.

(A) Heating operation Heating operation is started when the heating operation mode is selected by the selection switch while the operation switch of the operation panel is turned on. Then, during the heating operation, the defrosting operation is performed when it is determined by the frost determination unit that the outdoor heat exchange unit 16 has formed frost.

  First, during normal heating operation, the air conditioning controller closes the on-off valve 15a and switches the three-way valve 15b to a refrigerant flow path that connects the outlet side of the outdoor heat exchanger 16 and the inlet side of the accumulator 18, The cooling water pump 41 is operated so as to pressure-feed a predetermined flow rate of cooling water, and the three-way valve 42 of the cooling water circulation circuit 40 is switched to a cooling water circuit that flows around the radiator 43.

  Thereby, the heat pump cycle 10 is switched to the refrigerant flow path through which the refrigerant flows as shown by the solid line arrows in FIG. 1, and the cooling water circulation circuit 40 is changed to the cooling water circuit through which the cooling water flows as shown by the broken line arrows in FIG. Can be switched.

  With the configuration of the refrigerant flow path and the cooling water circuit, the air conditioning control device reads the detection signal of the above-described air conditioning control sensor group and the operation signal of the operation panel. And the target blowing temperature TAO which is the target temperature of the air which blows off into a vehicle interior is calculated based on the value of a detection signal and an operation signal. Furthermore, based on the calculated target blowing temperature TAO and the detection signal of the sensor group, the operating states of various air conditioning control devices connected to the output side of the air conditioning control device are determined.

  For example, the refrigerant discharge capacity of the compressor 11, that is, the control signal output to the electric motor of the compressor 11 is determined as follows. First, based on the target blowing temperature TAO, the target evaporator blowing temperature TEO of the indoor evaporator 20 is determined with reference to a control map stored in advance in the air conditioning control device.

  And based on the deviation of this target evaporator blowing temperature TEO and the blowing air temperature from the indoor evaporator 20 detected by the evaporator temperature sensor, the blowing air temperature from the indoor evaporator 20 is changed using a feedback control method. A control signal output to the electric motor of the compressor 11 is determined so as to approach the target evaporator outlet temperature TEO.

  For the control signal output to the servo motor of the air mix door 34, the target blowing temperature TAO, the blowing air temperature from the indoor evaporator 20, the discharge refrigerant temperature detected by the compressor 11 detected by the discharge refrigerant temperature sensor, and the like are used. Thus, the temperature of the air blown into the passenger compartment is determined so as to be a desired temperature for the passenger set by the passenger compartment temperature setting switch.

  Note that, during normal heating operation and defrosting operation, the opening degree of the air mix door 34 may be controlled so that the total air volume of the blown air blown from the blower 32 passes through the indoor condenser 12.

  Then, the control signal determined as described above is output to various air conditioning control devices. After that, until the operation of the vehicle air conditioner is requested by the operation panel, the above detection signal and operation signal are read at every predetermined control cycle → the target blowout temperature TAO is calculated → the operating states of various air conditioning control devices are determined -> Control routines such as control voltage and control signal output are repeated. Such a control routine is basically repeated in the same manner during other operations.

  In the heat pump cycle 10 during normal heating operation, the high-pressure refrigerant discharged from the compressor 11 flows into the indoor condenser 12. The refrigerant that has flowed into the indoor condenser 12 exchanges heat with the blown air that has been blown from the blower 32 and passed through the indoor evaporator 20 to dissipate heat. Thereby, blowing air is heated.

  Since the on-off valve 15a is closed, the high-pressure refrigerant flowing out of the indoor condenser 12 flows into the heating fixed throttle 13 and is decompressed and expanded. The low-pressure refrigerant decompressed and expanded by the heating fixed throttle 13 flows into the outdoor heat exchange unit 16. The low-pressure refrigerant flowing into the outdoor heat exchange unit 16 absorbs heat from the outside air blown by the blower fan 17 and evaporates.

  At this time, in the cooling water circulation circuit 40, since the cooling water is switched to the cooling water circuit that flows around the radiator unit 43, the cooling water radiates heat to the refrigerant flowing through the outdoor heat exchange unit 16, or the cooling water Does not absorb heat from the refrigerant flowing through the outdoor heat exchanger 16. That is, the cooling water does not thermally affect the refrigerant flowing through the outdoor heat exchange unit 16.

  The refrigerant flowing out of the outdoor heat exchange section 16 flows into the accumulator 18 because the three-way valve 15b is switched to the refrigerant flow path connecting the outlet side of the outdoor heat exchange section 16 and the inlet side of the accumulator 18. Gas-liquid separation. The gas-phase refrigerant separated by the accumulator 18 is sucked into the compressor 11 and compressed again.

  As described above, during normal heating operation, the blown air is heated by the amount of heat of the refrigerant discharged from the compressor 11 by the indoor condenser 12, so that the vehicle interior can be heated.

(B) Defrosting operation Next, the defrosting operation will be described. Here, as in the heat pump cycle 10 of the present embodiment, in the refrigeration cycle in which the outdoor heat exchange unit 16 exchanges heat between the refrigerant and the outside air to evaporate the refrigerant, the refrigerant evaporation temperature in the outdoor heat exchange unit 16 is frosted. If the temperature (specifically, 0 ° C.) or lower, frost formation may occur in the outdoor heat exchange unit 16.

  When such frost formation occurs, the outside air passage 70a of the heat exchanger 70 is blocked by frost, so that the heat exchange capability of the outdoor heat exchange unit 16 is significantly reduced. Therefore, in the heat pump cycle 10 of the present embodiment, the defrosting operation is executed when it is determined by the frosting determination means that frost formation has occurred in the outdoor heat exchange unit 16 during the heating operation.

  In this defrosting operation, the air conditioning controller stops the operation of the compressor 11 and stops the operation of the blower fan 17. Accordingly, during the defrosting operation, the flow rate of the refrigerant flowing into the outdoor heat exchange unit 16 is reduced and the air volume of the outside air flowing into the outdoor air passage 70a is reduced as compared with the normal heating operation.

  Further, the air-conditioning control device switches the three-way valve 42 of the cooling water circulation circuit 40 to a cooling water circuit that allows the cooling water to flow into the radiator section 43 as indicated by the broken line arrows in FIG. Thereby, a refrigerant | coolant does not circulate through the heat pump cycle 10, and the cooling water circulation circuit 40 is switched to the cooling water circuit through which a refrigerant | coolant flows as shown by the broken-line arrow of FIG.

  Accordingly, the heat quantity of the cooling water flowing through the cooling water tube 43a of the radiator section 43 is transferred to the outdoor heat exchange section 16 through the outer fin 50, and the outdoor heat exchange section 16 is defrosted. That is, defrosting that effectively uses the waste heat of the traveling electric motor MG is realized.

(C) Air-cooling operation Air-cooling operation is started when the air-cooling operation mode is selected by the selection switch while the operation switch of the operation panel is turned on. During this cooling operation, the air conditioning controller opens the on-off valve 15a and switches the three-way valve 15b to a refrigerant flow path that connects the outlet side of the outdoor heat exchanger 16 and the inlet side of the cooling expansion valve 19. Thereby, the heat pump cycle 10 is switched to the refrigerant | coolant flow path through which a refrigerant | coolant flows as shown by the solid line arrow of FIG.

  At this time, for the three-way valve 42 of the cooling water circulation circuit 40, when the cooling water temperature Tw becomes equal to or higher than the reference temperature, the cooling water circuit T is switched to a cooling water circuit that allows the cooling water to flow into the radiator unit 43. When the temperature becomes lower than the set reference temperature, the cooling water is switched to a cooling water circuit that flows around the radiator section 43. In FIG. 3, the flow of the cooling water when the cooling water temperature Tw becomes equal to or higher than the reference temperature is indicated by a broken line arrow.

  In the heat pump cycle 10 during the cooling operation, the high-pressure refrigerant discharged from the compressor 11 flows into the indoor condenser 12, exchanges heat with the blown air that is blown from the blower 32 and passes through the indoor evaporator 20, and dissipates heat. . The high-pressure refrigerant that has flowed out of the indoor condenser 12 flows into the outdoor heat exchanger 16 through the fixed throttle bypass passage 14 because the on-off valve 15a is open. The low-pressure refrigerant that has flowed into the outdoor heat exchange unit 16 exchanges heat with the outside air blown by the blower fan 17 to further dissipate heat.

  The refrigerant flowing out of the outdoor heat exchange unit 16 is switched to the refrigerant flow path in which the three-way valve 15b connects the outlet side of the outdoor heat exchange unit 16 and the inlet side of the cooling expansion valve 19, so that the expansion for cooling is performed. The valve 19 is decompressed and expanded. At this time, the throttle opening degree of the cooling expansion valve 19 is controlled so that the degree of supercooling of the refrigerant flowing out of the outdoor heat exchange unit 16 becomes a predetermined reference supercooling degree.

  The reference supercooling degree is a value determined so that the coefficient of performance of the cycle is substantially maximized. Therefore, in the present embodiment, the refrigerant in the most downstream side refrigerant collecting space of the heat exchanger 70 is also in the supercooled liquid phase state.

  The refrigerant flowing out of the cooling expansion valve 19 flows into the indoor evaporator 20, absorbs heat from the blown air blown by the blower 32, and evaporates. Thereby, blowing air is cooled. The refrigerant flowing out of the indoor evaporator 20 flows into the accumulator 18 and is separated into gas and liquid. The gas-phase refrigerant separated by the accumulator 18 is sucked into the compressor 11 and compressed again.

  As described above, during the cooling operation, the low-pressure refrigerant absorbs heat from the blown air and evaporates in the indoor evaporator 20, whereby the blown air is cooled and the vehicle interior can be cooled.

  In the vehicle air conditioner 1 of the present embodiment, various operations can be performed by switching the refrigerant flow path of the heat pump cycle 10 and the cooling water circuit of the cooling water circulation circuit 40 as described above. Furthermore, in this embodiment, since the characteristic heat exchanger 70 mentioned above is employ | adopted, in this heat exchanger 70, appropriate heat exchange between three types of fluids, a refrigerant | coolant, cooling water, and external air is realizable. .

  In other words, the heat exchanger 70 of the present embodiment includes the outer fin 50 that enables heat transfer between the refrigerant flowing through the refrigerant tube 16a and the cooling water flowing through the cooling water tube 43a. During the defrosting operation, the heat of the cooling water flowing through the cooling water tube 43 a can be transferred to the refrigerant tube 16 a of the outdoor heat exchange unit 16 through the outer fin 50.

  Therefore, the waste heat of the traveling electric motor MG can be effectively used for defrosting the outdoor heat exchange unit 16. At this time, in the present embodiment, the cooling water tube 43a is disposed only on the upstream heat exchanging portion 71 side where frost formation is likely to occur, so that efficient defrosting can be performed.

  Further, in the heat exchanger 70 of the present embodiment, the downstream heat exchanging portion 72 is configured only by the refrigerant tube 16a, so that a heat exchange region for exchanging heat between the refrigerant and the outside air during heating operation and cooling operation is provided. It can be secured sufficiently. Therefore, the heat absorption shortage or the heat radiation shortage of the refrigerant in the heat pump cycle 10 can be suppressed, and the deterioration of the coefficient of performance of the heat pump cycle 10 can be suppressed.

  Here, like the heat exchanger 70 of the present embodiment, the ratio of the number of refrigerant tubes 16a to the total number of tubes constituting the upstream heat exchange section 71 and the number of tubes constituting the downstream heat exchange section 72 are the same. When the ratio of the number of refrigerant tubes 16a to the total number of tubes is different, a communication path (fluid flow path) formed inside the tank portion 73 in order to connect the tank spaces 73a to 73c and the tubes 16a and 43a. ) Is likely to be complicated.

  On the other hand, according to the heat exchanger 70 of the present embodiment, since the tank portion 73 is configured by the plate header 731, the tank header 732, the intermediate plate 733, and the partition plate 734, the tank in the tank portion 73 A communication path that allows the spaces 73 a to 73 c to communicate with the tubes 16 a and 43 a can be formed by through holes that penetrate the front and back of the intermediate plate 733.

  At this time, among the three tank spaces 73a to 73c, the upstream end side tank space 73a can be easily communicated with the tubes constituting the upstream side heat exchange section 71. Similarly, the downstream end side tank space 73b can be easily communicated with the tubes constituting the downstream side heat exchange section 72.

  Further, with respect to the central tank space 73c, the central side communication path 733b is not limited to any of the tubes 16a and 43a constituting the upstream heat exchange unit 71 and the tubes 16a constituting the downstream heat exchange unit 72. It can be made to communicate easily by forming in the shape extended toward the center side from each tube 16a, 43a.

  Therefore, according to the heat exchanger 70 of the present embodiment, in the heat exchanger configured to be able to exchange heat between three types of fluids, the fluid flow path formed in the tank portion 73 can be easily formed. it can. As a result, various path configurations can be easily realized, and the heat exchange performance of the heat exchanger 70 as a whole can be improved.

  Moreover, in the heat exchanger 70 of this embodiment, since the heat insulation space 73d which suppresses heat transfer with the fluid in the center side tank header 732a and the fluid in the end side tank header 732b is formed, each tank space Unnecessary heat exchange between the fluids in 73a to 73c can be suppressed. This is extremely effective in a heat exchanger used as a condenser that condenses the refrigerant in the heat pump cycle 10 as in the cooling operation of the present embodiment.

  The reason is that the amount of heat exchange between the liquid-phase refrigerant condensed at a reduced temperature and the outside air is greatly reduced with respect to the amount of heat exchange between the gas-phase refrigerant and the outside air before the temperature is lowered. In other words, in the heat exchanger used as a condenser, if the region through which the condensed liquid phase refrigerant circulates increases among the refrigerant tubes constituting the heat exchange section, the heat exchange performance of the heat exchanger as a whole is increased. It will decline.

  For this reason, when the supercooling degree of the refrigerant | coolant in the most downstream refrigerant | coolant aggregate space falls by unnecessary heat exchange between the fluid in each tank space 73a-73c, it flows out from the outdoor heat exchange part 16. In order to set the refrigerant to be cooled to the reference supercooling degree, the throttle opening degree of the cooling expansion valve 19 is adjusted to increase the supercooling degree of the refrigerant flowing into the most downstream side refrigerant collecting space above the reference supercooling degree. I have to let you.

  However, in order to set the refrigerant flowing out of the outdoor heat exchanger 16 as the reference supercooling degree, if the supercooling degree of the refrigerant flowing into the most downstream side refrigerant collecting space is increased more than the reference supercooling degree, Of the refrigerant tubes constituting the exchange unit, the area through which the condensed liquid phase refrigerant flows is increased, and the heat exchange performance of the heat exchanger as a whole is lowered.

  In contrast, according to the heat exchanger 70 of the present embodiment, as described above, unnecessary heat exchange between the fluids in the tank spaces 73a to 73c can be suppressed. It can suppress that exchange performance deteriorates.

  Further, in the heat exchanger 70 of the present embodiment, when viewed from the outside air flow direction X, the most downstream side heat medium assembly space and the most downstream side heat medium assembly space for collecting the heat medium flowing out to the outside are superposed. Are arranged to be.

  Therefore, during the cooling operation in which the heat exchanger 70 functions as a condenser, the temperature difference between the cooling water in the most downstream heat medium assembly space and the refrigerant in the most downstream refrigerant assembly space can be reduced, and the most downstream Unnecessary heat exchange between the cooling water in the side heat medium assembly space and the refrigerant in the most downstream side refrigerant assembly space can be effectively suppressed.

  Further, in the heat exchanger 70 of the present embodiment, when viewed from the outside air flow direction X, the most downstream refrigerant assembly space and the refrigerant in the most downstream refrigerant assembly space rather than the refrigerant immediately after flowing in from the outside, The intermediate temperature refrigerant space into which the refrigerant having a small temperature difference flows is superposed.

  Therefore, during the cooling operation in which the heat exchanger 70 functions as a condenser, the temperature difference between the refrigerant in the intermediate temperature refrigerant space and the refrigerant in the most downstream refrigerant collecting space can be reduced, and the intermediate temperature refrigerant space can be reduced. Unnecessary heat exchange between the internal refrigerant and the refrigerant in the most downstream side refrigerant assembly space can be effectively suppressed.

  Moreover, in the heat exchanger 70 of this embodiment, since the most downstream side refrigerant | coolant gathering space is formed in the upstream end side tank space 73a, at the time of the cooling operation in which the heat exchanger 70 functions as a condenser, the most downstream side refrigerant | coolant is used. In the fourth path 16P4 of FIG. 9 connected to the collective space, the refrigerant can be efficiently cooled by the outside air before heat exchange with the refrigerant or the cooling water.

  Moreover, in the heat exchanger 70 of this embodiment, since the center side tank header 732a and the end side tank header 732b are comprised by a different member, they are arrange | positioned in the tank part 73 along with the flow direction X of external air. The three tank spaces 73a to 73c can be easily formed. Furthermore, the heat insulation space 73d that suppresses the heat transfer between the fluid in the center side tank header 732a and the fluid in the end side tank header 732b can be easily formed.

  In addition, the degree of freedom in designing the shape or size (volume) of the central tank space 73c can be improved. This is extremely effective in a configuration in which three tank spaces 73a to 73c are provided in the tank portion 73 and the spaces for arranging the tank spaces 73a to 73c tend to be narrow, as in the heat exchanger 70 of the present embodiment. is there.

(Second Embodiment)
In the present embodiment, an example in which the configuration of the heat exchanger 70 is changed as illustrated in the cross-sectional view of FIG. 10 will be described. FIG. 10 is a view of a cross section corresponding to FIG. 7 of the first embodiment as viewed obliquely from the upper side of the tank portion 73. In FIG. 10, the same or equivalent parts as those in the first embodiment are denoted by the same reference numerals. The same applies to the following drawings.

  Specifically, in the present embodiment, as shown in FIG. 10, a tank header 732 in which a center side tank header 732a, an end side tank header 732b, and a heat insulating space 73d are integrally configured is employed. Such a tank header 732 can be formed by extrusion molding or pultrusion molding.

  Other configurations and operations of the heat exchanger 70 and the heat pump cycle 10 are the same as those in the first embodiment. Therefore, even if the heat exchanger 70 is configured as in the present embodiment, the same effect as in the first embodiment can be obtained.

  In addition, as shown in a modification in FIG. 11, also when the tank header 732 is formed by extrusion molding or pultrusion molding, the shape or size (volume) of each of the tank spaces 73a to 73c can be changed. FIG. 11 is a drawing corresponding to FIG. 7 of the first embodiment. Further, as shown in FIG. 11, the intermediate plate 733 and the partition plate 734 may be formed by pressing a flat metal.

(Third embodiment)
In the present embodiment, an example in which the configuration of the heat exchanger 70 is changed as shown in the cross-sectional view of FIG. 12 will be described. FIG. 12 is a drawing corresponding to FIG. 10 of the second embodiment. Specifically, in this embodiment, as shown in FIG. 12, the end-side tank header 732b is formed by bending a flat metal into a two-section cross section.

  Furthermore, in the present embodiment, the central valley of the end-side tank header 732b is joined directly to the central valley (recess) of the end-side tank header 732b by joining the second member 732d of the central-side tank header having an arcuate cross section. A central tank space 73c is formed between the outer peripheral surface of the portion (concave portion) and the inner peripheral surface of the second member 732d. Therefore, the heat insulation space 73d described in the above embodiment is not configured in the tank portion 73 of the present embodiment.

  Other configurations and operations of the heat exchanger 70 and the heat pump cycle 10 are the same as those in the first embodiment. Therefore, even if the heat exchanger 70 is configured as in the present embodiment, appropriate heat exchange between the three types of fluids, that is, the refrigerant, the cooling water, and the outside air, can be realized as in the first embodiment. Furthermore, the fluid flow path formed in the tank part 73 can be formed easily.

  In addition, the heat insulation space 73d is not formed in the tank portion 73 of the heat exchange unit 70 of the present embodiment. For this reason, it is difficult to obtain the effect of suppressing unnecessary heat exchange between the fluids in the tank spaces 73a to 73c.

  Therefore, as shown in the modification of FIG. 13, the second member 732d of the central tank header is provided with a protrusion 732e that protrudes toward the end side tank header 732b, and this protrusion 732e is provided on the end side tank header 732b. You may make it join. The protrusion 732e is formed in a conical shape or a hemispherical shape, and is in point contact with the end-side tank header 732b. FIG. 13 is a drawing corresponding to FIG. 11 of the second embodiment.

  Thereby, the junction area (contact area) of the 2nd member 732d of a center side tank header and the end side tank header 732b is reduced, and the unnecessary heat exchange between the fluids in each tank space 73a-73c is suppressed. can do.

(Fourth embodiment)
This embodiment demonstrates the example which changed the flow aspect of the refrigerant | coolant in the heat exchanger 70 and a cooling water as shown in FIG. 14 with respect to 1st Embodiment. Specifically, in the heat exchanger 70 of the present embodiment, the tank spaces 73a and 73b are divided in the longitudinal direction into an upstream end side tank space 73a and a downstream end side tank space 73b of the tank part 73 on the lower side. A separator (not shown) is arranged.

  And as shown in FIG. 14, the refrigerant | coolant inflow port 161 which flows in a refrigerant | coolant to one downstream end side tank space 73b divided | segmented with the separator is provided in the longitudinal direction one end side of the tank part 73 of the downward side, A refrigerant outflow port 162 through which refrigerant flows out from one upstream end side tank space 73a divided by the separator is provided.

  Similarly, a cooling water inflow port 431 for allowing cooling water to flow into the central tank space 73c of the upper tank portion 73 is provided on the other longitudinal end side of the upper tank portion 73, and the lower tank portion. A cooling water outflow port 432 through which cooling water flows out from the central tank space 73c of the tank part 73 on the lower side is provided on one end side in the longitudinal direction of 73.

  And in the heat exchanger 70 of this embodiment, as shown by the thick solid line arrow of FIG. 14, the refrigerant | coolant which flowed into the downstream end side tank space 73b of the tank part 73 of the downward side from the refrigerant | coolant inflow port 161 is downstream heat | fever. It is distributed to the refrigerant tube 16a group of a part of the exchange part 72 (right side in FIG. 14, that is, the refrigerant inflow port 161, the refrigerant outflow port 162, and the cooling water outflow port 432 side), and the downstream end of the upper tank part 73 Collect in the side tank space 73b.

  The refrigerant that has gathered in the downstream end side tank space 73b of the upper tank portion 73 flows from the right side to the left side in FIG. 14, and the rest of the downstream heat exchange portion 72 (left side in FIG. 14, ie, the cooling water inflow port 431). Side) refrigerant tube 16a group, and gathers in the downstream end side tank space 73b of the tank part 73 on the lower side.

  The refrigerant collected in the downstream end side tank space 73b of the lower side tank part 73 passes through the communication path formed in the intermediate plate of the lower side tank part 73 and the upstream end side tank space of the lower side tank part 73. It flows into 73a.

  Further, the refrigerant that has flowed into the upstream end side tank space 73a of the lower tank portion 73 is distributed to a part of the downstream side heat exchange portion 72 (left side in FIG. 14) as a refrigerant tube 16a group. The tank portion 73 gathers in the upstream end side tank space 73a.

  The refrigerant that has gathered into the upstream end side tank space 73a of the upper side tank portion 73 flows from the left side to the right side in FIG. 14, and is distributed to the remaining refrigerant tube 16a group of the upstream side heat exchange unit 71, Gathers into the upstream end side tank space 73a of the side tank portion 73. The refrigerant that has gathered into the upstream end side tank space 73 a of the lower tank portion 73 flows out from the refrigerant outflow port 162.

  In other words, in the heat exchanger 70 of the present embodiment, as a path configuration through which the refrigerant flows, the refrigerant distributed from the right side of the downstream end side tank space 73b of the lower side tank unit 73 is downstream of the upper side tank unit 73. The first path 16P1 that collects to the right side of the end side tank space 73b, the refrigerant distributed from the left side of the downstream end side tank space 73b of the upper side tank unit 73, and the downstream end side tank space 73b of the lower side tank unit 73 A second path 16P2 that collects to the left side, a third system that collects refrigerant distributed from the left side of the upstream end side tank space 73a of the lower tank part 73 to the left side of the upstream end side tank space 73a of the upper side tank part 73. The refrigerant distributed from the right side of the upstream end side tank space 73a of the path 16P3 and the upper side tank part 73 is transferred to the right side of the upstream end side tank space 73a of the lower side tank part 73. The third path 16P4 is formed engaged.

  Therefore, in the present embodiment, the space on the left side of the upstream end side tank space 73a of the lower tank portion 73 (the space communicating with the refrigerant outflow port 162) collects the refrigerant that flows out of the heat exchanger 70. A downstream refrigerant collecting space is formed.

  On the other hand, with respect to the cooling water, as shown by the thick broken line arrows in FIG. 14, the cooling water flowing into the central tank space 73c of the upper tank portion 73 from the cooling water inflow port 431 is distributed to the cooling water tube 43a. As a result, the tank portion 73 gathers into the central tank space 73c of the lower tank portion 73. The cooling water gathered into the central tank space 73 c of the lower tank portion 73 flows out from the cooling water outflow port 432.

  In other words, in the heat exchanger 70 of the present embodiment, as a path configuration through which cooling water flows, the refrigerant distributed from the central tank space 73c of the upper tank portion 73 is used as the central tank of the lower tank portion 73. A first path 43P1 for assembling into the space 73c is formed.

  Furthermore, in the present embodiment, the central tank space 73c of the lower tank portion 73 forms a most downstream heat medium assembly space in which cooling water that flows out of the heat exchanger 70 is collected. Further, when viewed from the flow direction X of the outside air, the most downstream heat medium assembly space and the most downstream refrigerant assembly space are arranged to be superposed.

  Other configurations and operations of the heat exchanger 70 and the heat pump cycle 10 are the same as those in the first embodiment. Therefore, even if the heat exchanger 70 is configured as in the present embodiment, the same effect as in the first embodiment can be obtained.

  Note that, in the heat exchanger 70 of the present embodiment, when viewed from the outside air flow direction X, each tank space is not disposed so as not to superpose the most downstream refrigerant collecting space and the intermediate temperature refrigerant space. Although the effect of suppressing unnecessary heat exchange between the fluids in the fluids 73a to 73c is reduced, when the heat exchanger 70 functions as a condenser, the first path 16P1 through which the highest temperature refrigerant flows and the highest temperature It arrange | positions so that it may superpose | polymerize with 4th path | pass 16P4 through which a high refrigerant | coolant flows.

  Thereby, the temperature distribution of the external air heat-exchanged with the heat exchanger 70 can be suppressed. This is effective, for example, when the heat exchanger 70 is used as a heat exchanger for heating that heats the blown air as the third fluid, as shown in the fifth embodiment. Further, the structure of the tank portion 73 described with reference to FIGS. 2 and 3 may be applied to the heat exchanger 70 of the present embodiment.

(Fifth embodiment)
In the above-described embodiment, the example in which the heat exchanger 70 performs heat exchange between the three kinds of fluids of the refrigerant, the cooling water, and the outside air has been described. However, in the present embodiment, as illustrated in the overall configuration diagram of FIG. An example in which the configuration of the heat pump cycle 10 is changed and heat exchange between the three types of fluids of the refrigerant, the cooling water, and the blown air is performed in the heat exchanger 70 will be described. Further, in the heat pump cycle 10 of the present embodiment, in addition to the heating operation and the cooling operation, a waste heat recovery operation for heating the vehicle interior by using the waste heat of the traveling electric motor MG can be performed.

  Specifically, in the heat pump cycle 10, the indoor condenser 12 of the first embodiment is abolished, and the composite heat exchanger 70 of the first embodiment is arranged in the casing 31 of the indoor air conditioning unit 30. ing. And among this heat exchanger 70, the outdoor heat exchange part 16 of 1st Embodiment is functioned as a structure corresponded to the indoor condenser 12 of 1st Embodiment. Hereinafter, the part functioning as the indoor condenser 12 in the heat exchanger 70 is referred to as an indoor condenser 120.

  Furthermore, in the heat pump cycle 10 of the present embodiment, as a configuration corresponding to the outdoor heat exchange unit 16 of the first embodiment, a single heat that exchanges heat between the refrigerant circulating inside and the outside air blown from the blower fan 17 is used. An outdoor heat exchanger 160 composed of an exchanger is provided. Other configurations are the same as those of the first embodiment.

  Next, the operation of this embodiment in the above configuration will be described. In the heat pump cycle 10 of the present embodiment, the same heating operation and cooling operation as in the first embodiment can be performed, and the waste heat recovery operation can be performed. The waste heat recovery operation is executed when the cooling water temperature Tw becomes equal to or higher than a predetermined reference waste heat recovery temperature (60 ° C. in the present embodiment) during the heating operation.

  In the waste heat recovery operation, as in the normal heating operation, the air conditioning control device closes the on-off valve 15a and connects the three-way valve 15b to the outlet side of the outdoor heat exchanger 16 and the inlet side of the accumulator 18. Switch to the flow path. Further, the cooling water pump 41 is operated so as to pump a predetermined flow rate of cooling water, and the three-way valve 42 of the cooling water circulation circuit 40 is switched to a cooling water circuit in which the cooling water flows into the radiator section 43.

  As a result, the heat pump cycle 10 is switched to the refrigerant flow path through which the refrigerant flows as shown by the solid line arrows in FIG. 15, and the cooling water circulation circuit 40 is changed to the cooling water circuit through which the cooling water flows as shown by the broken line arrows in FIG. Can be switched.

  Accordingly, the high-pressure and high-temperature refrigerant discharged from the compressor 11 flows into the indoor condensing unit 120 of the heat exchanger 70 and exchanges heat with the air blown into the vehicle interior, as in normal heating operation. Thereby, vehicle interior blowing air is heated. Furthermore, in this embodiment, since the cooling water circulation circuit 40 is switched to a cooling water circuit that allows cooling water to flow into the radiator section 43 of the heat exchanger 70, the air blown into the vehicle interior is cooled by the cooling water that has flowed into the radiator section 43. Heated with heat exchange.

  The vehicle interior blown air that has flowed out of the indoor condensing unit 120 of the heat exchanger 70 flows into the heating fixed throttle 13, is decompressed and expanded, and flows into the outdoor heat exchanger 160. The low-pressure refrigerant flowing into the outdoor heat exchanger 160 absorbs the heat of the outside air blown by the blower fan 17 and evaporates. Subsequent operations are the same as in normal heating operation.

  As described above, during the waste heat recovery operation, the air blown into the vehicle interior is heated by the heat of the refrigerant discharged from the compressor 11 by the indoor condenser 12 and the heat of the cooling water circulating in the cooling water circulation circuit 40, The passenger compartment can be heated. That is, it is possible to realize heating in the vehicle interior that effectively uses the waste heat of the traveling electric motor MG.

  Furthermore, according to the configuration of the heat pump cycle 10 of the present embodiment, the heat exchange between the cooling water and the air blown into the passenger compartment can be performed, so that the operation of the heat pump cycle 10 (specifically, the compressor 11) is stopped. Even in such a case, heating of the passenger compartment can be realized. Moreover, even when the temperature of the refrigerant discharged from the compressor 11 is low and the heating capacity of the heat pump cycle 10 is low, heating of the passenger compartment can be realized.

  Of course, you may apply the heat exchanger 70 demonstrated in 2nd-4th embodiment with respect to the heat pump cycle 10 of this embodiment. Furthermore, if the heat exchanger 70 described in the fourth embodiment is employed, the temperature distribution of the air blown into the passenger compartment can be suppressed during the heating operation or the waste heat recovery operation.

(Other embodiments)
The present invention is not limited to the above-described embodiment, and can be variously modified as follows without departing from the spirit of the present invention.

  (1) In the above-described embodiment, the ratio of the number of the refrigerant tubes 16a to the total number of tubes constituting the upstream heat exchange unit 71 is set to the refrigerant for the total number of tubes constituting the downstream heat exchange unit 72. Although the example which made it smaller than the number ratio of the tube 16a was demonstrated, a number ratio is not limited to this.

  For example, the number ratio in the upstream heat exchange section 71 may be larger than the number ratio in the downstream heat exchange section 72, the number ratio in the upstream heat exchange section 71 and the number ratio in the downstream heat exchange section 72, May be equivalent.

  Furthermore, in the above-described embodiment, the example in which the upstream heat exchange unit 71 is configured by alternately arranging the refrigerant tubes 16a and the cooling water tubes 43a has been described. However, in each of the heat exchange units 71 and 72, The arrangement of the tubes 16a and 43a is not limited to this, and may be appropriately determined according to the amount of heat exchange between the three types of fluids.

  (2) In the above-described embodiment, the path configuration of the heat exchanger 70 is the one described with reference to FIGS. 9 and 14, but the path configuration of the heat exchanger 70 is not limited to this. Various path configurations can be employed.

  At this time, in order to suppress unnecessary heat exchange between the fluids in the tank spaces 73a to 73c, when viewed from the flow direction X of the outside air, the most downstream side refrigerant assembly space and the most downstream side heat medium assembly. It is desirable that the space is arranged so as to be polymerized, and the most downstream side refrigerant collecting space and the intermediate temperature refrigerant space are arranged so as to be polymerized.

  In the above-described embodiment, the refrigerant inflow port 161, the refrigerant outflow port 162, the cooling water inflow port 431, and the cooling water outflow port 432 are formed in the cylindrical side surface of the tank portion 73 formed in a cylindrical shape, or in the longitudinal direction end. Although the example arrange | positioned in the cover member which is provided in a part and block | closes each tank space 73a-73c was demonstrated, arrangement | positioning of these inflow / outflow ports is not limited to this.

  (3) In the heat pump cycle 10 of the first embodiment described above, an example in which an electric variable throttle mechanism is employed as the cooling expansion valve 19 has been described. However, as a cooling decompression unit, an orifice or a capillary tube is used. A fixed iris for cooling may be adopted. Further, the cooling fixed throttle is preferably set so that the degree of supercooling of the refrigerant flowing out of the outdoor heat exchanger 16 of the heat exchanger 70 during the cooling operation becomes a predetermined reference supercooling degree.

  Similarly, in the heat pump cycle of the fifth embodiment, as the fixed throttle 13 for heating, the degree of supercooling of the refrigerant flowing out from the indoor condensing part 120 of the heat exchanger 70 during the heating operation becomes a predetermined reference supercooling degree. Those set to are desirable. Furthermore, instead of the heating fixed throttle 13, a variable throttle mechanism similar to the cooling expansion valve 19 is adopted, and the degree of supercooling of the refrigerant flowing out from the indoor condensing part 120 of the heat exchanger 70 during the heating operation is determined in advance. The throttle opening may be controlled so that the reference supercooling degree is achieved.

  Of course, the refrigerant flowing out of the outdoor heat exchange unit 16 or the indoor condensing unit 120 of the heat exchanger 70, that is, the refrigerant in the most downstream side refrigerant assembly space does not necessarily have to be in a liquid phase state having a supercooling degree. Further, it may be in a saturated liquid phase state, or may be in a gas-liquid two phase state with extremely low dryness.

  (4) In the above-described embodiment, the refrigerant of the heat pump cycle 10 is adopted as the first fluid, the cooling water of the cooling water circulation circuit 40 is adopted as the second fluid, and the outside air or the blown air is adopted as the third fluid. Although the example which did was demonstrated, the 1st-3rd fluid is not limited to this. For example, cooling water of an internal combustion engine (engine) may be adopted as the second fluid. In this case, the internal combustion engine (engine) is an external heat source.

  Further, when the heat pump cycle 10 to which the heat exchanger 70 of the present invention is applied is applied to a stationary air conditioner, a cold storage, a cooling / heating device for a vending machine, etc., the compression of the heat pump cycle 10 is used as the second fluid. You may employ | adopt the cooling water which cools the engine, electric motor, other electric equipment, etc. as a drive source of a machine.

  Moreover, although the above-mentioned embodiment demonstrated the example which applied the heat exchanger 70 of this invention to the heat pump cycle (refrigeration cycle), application of the heat exchanger 70 of this invention is not limited to this. That is, the present invention can be widely applied to devices that exchange heat between three types of fluids.

  For example, it can be applied as a heat exchanger applied to a cooling system. The first fluid is a heat medium that absorbs the amount of heat of the first device that generates heat during operation, the second fluid is the heat medium that absorbs the amount of heat of the second device that generates heat during operation, and the third fluid The fluid may be outdoor air.

  The above-mentioned three types of fluids not only mean fluids having different physical properties and components, but also fluids having the same physical properties and components but having different states such as temperature, gas phase, and liquid phase. Including meaning. Therefore, the first fluid may be the high-pressure side refrigerant of the heat pump cycle 10 and the second fluid may be the low-pressure side refrigerant of the heat pump cycle 10.

  (5) In the above-described embodiment, the example in which the electric three-way valve 42 is employed as the circuit switching unit that switches the cooling medium circuit of the cooling water circulation circuit 40 has been described, but the circuit switching unit is not limited thereto. For example, a thermostat valve may be employed. The thermostat valve is a cooling medium temperature responsive valve configured by a mechanical mechanism that opens and closes a cooling medium passage by displacing a valve body by a thermo wax (temperature-sensitive member) whose volume changes with temperature.

  (6) In the heat pump cycle 10 of the first embodiment described above, the example in which the blown air is heated by exchanging heat between the high-pressure refrigerant and the blown air in the indoor condenser 12 has been described. For example, a heat medium circulation circuit that circulates the heat medium is provided, and the heat medium circulation circuit is heated by a water-refrigerant heat exchanger and a water-refrigerant heat exchanger that exchange heat between the high-pressure refrigerant and the heat medium. A heat exchanger for heating that heats the blown air by exchanging heat between the heated medium and the blown air may be disposed.

  In other words, the blown air may be indirectly heated through the heat medium using the high-pressure refrigerant as a heat source. Furthermore, when applied to a vehicle having an internal combustion engine, the heat medium circulation circuit may be circulated using cooling water of the internal combustion engine as a heat medium. Moreover, in an electric vehicle, you may make it distribute | circulate a heat-medium circulation circuit by using the cooling water which cools a battery and an electric equipment as a heat medium.

16a Refrigerant tube (first tube)
43a Cooling water tube (second tube)
70a Outside air passage (third fluid passage)
71 Upstream heat exchange section (heat exchange section)
72 Downstream heat exchanger (heat exchanger)
73 Tank part 731 Plate header 732 Tank header 733 Intermediate plate 734 Partition plate

Claims (8)

The first tube (16a) through which the first fluid circulates and the second tube (43a) through which the second fluid circulates are stacked, and the first fluid and the third fluid are exchanged in heat and the first fluid is exchanged. A heat exchange section (71, 72) for exchanging heat between two fluids and the third fluid;
Tank spaces (73a to 73c) for collecting or distributing one of the first fluid flowing through the first tube (16a) and the second fluid flowing through the second tube (43a) are formed. A tank part (73),
A space formed between adjacent tubes of the first tube (16a) and the second tube (43a) forms a third fluid passage (70a) through which the third fluid flows,
In the third fluid passage (70a), heat exchange between the first fluid and the third fluid and heat exchange between the second fluid and the third fluid are promoted, and the first tube (16a) is promoted. An outer fin (50) that enables heat transfer between the first fluid flowing through the second tube (43a) and the second fluid flowing through the second tube (43a);
As said heat exchange part (71, 72), the upstream heat exchange part (71) arrange | positioned upstream of the flow direction (X) of the said 3rd fluid, and the downstream of the flow direction (X) of the said 3rd fluid A downstream heat exchange section (72) disposed on the side,
The first tube (16a) is disposed in both the upstream heat exchange section (71) and the downstream heat exchange section (72),
The second tube (43a) is disposed on at least one of the upstream heat exchange section (71) and the downstream heat exchange section (72),
When viewed from the flow direction (X) of the third fluid, the upstream heat exchange section (71) and the downstream heat exchange section (72) are superposed on each other. It is arranged so that there are both a part to be arranged and a part to be arranged so that the first tube (16a) and the second tube (43a) are polymerized,
The tank part (73) includes a plate header (731) to which the first and second tubes (16a, 43a) are joined, a tank header (732) that forms the tank spaces (73a to 73c) inside, An intermediate plate (733) formed with a plurality of communication passages (733a, 733b) for communicating the first and second tubes (16a, 43a) and the tank spaces (73a-73c), and the communication passages (733a, 733b) and a partition plate (734) in which a plurality of communication holes (734a to 734c) for communicating the tank spaces (73a to 73c) are formed,
Furthermore, in the tank part (73), three tank spaces (73a to 73c) arranged side by side in the flow direction (X) of the third fluid are formed,
Of the three tank spaces (73a to 73c), the one disposed in the center in the flow direction (X) of the third fluid is a central tank space (73c), and the plurality of communication passages (733a, 733b). When one of the first and second tubes (16a, 43a) and the central tank space (73c) communicate with each other as a central communication path (733b),
The central side communication path (733b) is formed by a through hole penetrating the front and back of the intermediate plate (733), and when viewed from the longitudinal direction of the first and second tubes (16a, 43a). Further, the heat exchanger is formed in a shape extending from the position where it overlaps with the first and second tubes (16a, 43a) toward the central tank space (73c). The tank header (732) includes at least a central tank header (732a) that forms the central tank space (73c) and an end that forms tank spaces (73a, 73b) other than the central tank space (73c). Side tank header (732b)
Between the outer peripheral surface of the central tank header (732a) and the outer peripheral surface of the end tank header (732b), the fluid in the central tank header (732a) and the end tank header (732b) The heat exchanger according to claim 1, wherein a heat insulating space (73 d) that suppresses heat transfer with the fluid is formed. The tank header (732) includes at least a central tank header (732a) that forms the central tank space (73c) and an end that forms tank spaces (73a, 73b) other than the central tank space (73c). Side tank header (732b)
The heat exchanger according to claim 1 or 2, wherein the central tank header (732a) and the end tank header (732b) are formed of different members. A heat exchanger used as a condenser for condensing refrigerant in a vapor compression refrigeration cycle (10),
Of the three tank spaces (73a to 73c), the one disposed on the most upstream side in the flow direction (X) of the third fluid is defined as an upstream end side tank space (73a), and the flow direction of the third fluid When the downstream end of (X) is the downstream end tank space (73b),
The first fluid is a refrigerant of the refrigeration cycle (10);
The second fluid is a heat medium that absorbs the amount of heat of the external heat source,
The third fluid is outdoor air;
The central tank space (73c) forms a space for collecting or distributing the heat medium,
At least one of the upstream end side tank space (73a) and the downstream end side tank space (73b) forms a most downstream side refrigerant collecting space for collecting the refrigerant flowing out to the outside. The heat exchanger according to any one of claims 1 to 3.   The heat exchanger according to claim 4, wherein the upstream end side tank space (73a) forms a most downstream side refrigerant collecting space for collecting the refrigerant flowing out to the outside.   The heat exchanger according to claim 4 or 5, wherein the refrigerant is in a supercooled liquid phase state in the most downstream refrigerant collecting space.   Of the central tank space (73c), a space that is overlapped with the most downstream refrigerant collecting space when viewed from the flow direction (X) of the outdoor air collects the heat medium that flows out to the outside. The heat exchanger according to any one of claims 4 to 6, wherein a most downstream heat medium assembly space is formed.   Of the downstream end side tank space (73b), when viewed from the flow direction (X) of the outdoor air, the space overlapped with the most downstream side refrigerant assembly space is more than the refrigerant just after flowing in from the outside. 8. The heat according to claim 4, further comprising an intermediate temperature refrigerant space into which a refrigerant having a small temperature difference with respect to the refrigerant in the most downstream refrigerant collecting space is introduced. Exchanger.

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