JP5413433B2 - 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 the heat exchanger disclosed in Patent Document 1, heat exchange between the refrigerant of the refrigeration cycle apparatus and outdoor air (outside air) and heat exchange between the refrigerant and cooling water for cooling the engine are performed. There is disclosed a composite heat exchanger configured so as to be able to do this.

  Specifically, in the heat exchanger of Patent Document 1, a plurality of linear refrigerant tubes whose both ends are connected to a refrigerant tank that collects and distributes refrigerant are stacked, and the stacked refrigerant tubes A heat pipe whose one end is connected to a cooling water tank through which cooling water flows is arranged in parallel with the refrigerant tube, and heat exchange is promoted in an outside air passage formed between the refrigerant tube and the heat pipe. It is the composition which arranged the fin.

  And in the refrigerating cycle device of patent documents 1, this compound type heat exchanger makes the refrigerant absorb the heat which outside air has, and the heat which cooling water has (namely, waste heat of an engine), and the evaporator which evaporates a refrigerant When functioning as, the frosting of the heat exchanger is suppressed by the waste heat of the engine transmitted from the heat pipe.

JP-A-11-157326

  By the way, in the heat exchanger of patent document 1, in order to implement | achieve heat exchange with the refrigerant | coolant and external air which were mentioned above, and heat exchange with a refrigerant | coolant and cooling water, a refrigerant | coolant tank and a cooling water tank are made into the flow direction of external air. The heat pipes are arranged between a plurality of refrigerant tubes extending in a straight line by arranging them adjacent to each other and making the heat pipes bend in the vicinity of the cooling water tank.

  However, disposing the refrigerant tank and the cooling water tank adjacent to each other in the flow direction of the outside air causes an increase in the size of the heat exchanger in the flow direction of the outside air. Furthermore, in the heat exchanger of patent document 1, since the thing of the complicated shape curved in the cooling water tank vicinity must be employ | adopted as a heat pipe, the productivity of a heat exchanger will be deteriorated.

  An object of this invention is to improve the productivity of the heat exchanger which can perform heat exchange between three types of fluid in view of the said point.

To achieve the above object, according to the first aspect of the present invention, the first tube extends in the stacking direction of the plurality of first tubes (61) and the plurality of first tubes (61) through which the first fluid flows. A first tank section (62) that collects or distributes the first fluid that circulates through (61), and performs heat exchange between the first fluid and the third fluid that flows around the first tube (61). A heat exchange section (60), a plurality of second tubes (71) through which the second fluid flows, and a second pipe (71) that extends in the stacking direction of the plurality of second tubes (71) and flows through the second tubes (71). A second heat exchanging unit (70) having a second tank unit (72) for collecting or distributing the fluid and exchanging heat between the second fluid and the third fluid flowing around the second tube (71); Prepared,
The first tube (61) and the second tube (71) are disposed between the first tank part (62) and the second tank part (72), and at least one of the plurality of first tubes (61). Is disposed between the plurality of second tubes (71), and at least one of the plurality of second tubes (71) is disposed between the plurality of first tubes (61). ) And the second tube (71) form a third fluid passage (16a) through which the third fluid flows, and the third fluid passage (16a) includes both Heat exchange between the first fluid flowing through the first tube (61) and the second fluid flowing through the second tube (71) is possible. Outer fins (50) are arranged,
The first tube (61) is provided with a first turn part (61e) that changes the flow direction of the first fluid, and the second tube (71) has a second turn that changes the flow direction of the second fluid. Part (71e) is provided, the first turn part (61e) is positioned closer to the second tank part (72) than the first tank part (62), and the second turn part (71e) is The heat exchanger is positioned closer to the first tank part (62) than the two tank parts (72).

  According to this, about the 1st fluid and the 3rd fluid, heat exchange can be carried out via the 1st tube (61) and the outer fin (50), and about the 2nd fluid and the 3rd fluid, Heat exchange can be performed through the two tubes (71) and the outer fins (50). Furthermore, the first fluid and the second fluid can be heat exchanged via the outer fin (50). That is, heat exchange can be performed between the three types of fluids.

  Further, the first tube (61) and the second tube (71) are disposed between the first tank part (62) and the second tank part (72), and the first tube (61) and the second tube (71). ), The third fluid passage (16a) is formed by the space formed between the first tank portion (62) and the second tank portion (72). . Therefore, it can suppress that the heat exchanger as a whole enlarges in the flow direction of the third fluid.

  Moreover, the first turn portion (61e) of the first tube (61) is positioned closer to the second tank portion (72) than the first tank portion (62), and the second turn portion of the second tube (71). (71e) is positioned closer to the first tank part (62) than the second tank part (72), so that the first tube (61) is connected to the first tank part (62), The thing of the same shape as what connected the 2nd tube (71) to the 2nd tank part (72) is employable.

  As a result, it is possible to improve the productivity of a heat exchanger that can exchange heat between three types of fluids without causing an increase in size. Note that the 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 fluid states such as temperature, gas phase, and liquid phase. Meaning included. Therefore, the first to third fluids in this claim are not limited to fluids having different physical properties and components.

  Here, when the temperature of the first fluid introduced into the first heat exchange unit (60) is different from the temperature of the second fluid introduced into the second heat exchange unit (70), the first tube (61) and Since the amount of thermal strain (thermal expansion amount) generated in the second tube (71) is different, the dimensions of the first tube (61) and the second tube (71) may change. Such a change in the dimensions of the tubes (61, 71) can be a factor causing damage to the heat exchanger.

  Therefore, in the invention according to claim 2, in the heat exchanger according to claim 1, the temperature of the first fluid introduced into the first heat exchange section (60) is applied to the second heat exchange section (70). The outer fin (50) is different from the temperature of the second fluid to be introduced, and the first and second tubes (61, 71) and the first and second tubes (61, 71) disposed adjacent to the first and second tubes (61, 71). 71), and is arranged in a space formed between the two.

  According to this, since heat exchange of each fluid is promoted by the outer fin (50), the temperature difference between the first fluid and the second fluid can be reduced, and the first tube (61) and the second tube The difference in thermal strain amount of (71) can be relaxed (reduced). As a result, damage to the heat exchanger can be suppressed.

  In addition, the “space formed between the first and second tubes (61, 71) and the first and second tubes (61, 71) arranged adjacent to the first and second tubes” in this claim is: Between the first tube (61) and the first tube (61) or the second tube (72) adjacent to the first tube (61), the second tube (71), and the second tube (71 ) Means a space formed between the first tube (61) and the second tube (72) adjacent to each other.

  Further, “introduction” and “derivation” in the present claims mean the movement state of the refrigerant in the heat exchanger, and “inflow” and “outflow” mean the movement state of the refrigerant in each tube (61, 71). doing.

  According to a third aspect of the present invention, in the heat exchanger according to the first or second aspect, the first tube (61) and the second tube (71) are both the first tank portion (62) and the second tank. It is characterized by being fixed to both parts (72).

  According to this, since both the 1st tube (61) and the 2nd tube (71) are being fixed to the 1st tank part (62) and the 2nd tank part (72), as the whole heat exchanger The mechanical strength can be increased. Furthermore, the outer fin (50) disposed in the third fluid passage (16a) formed between the first tube (61) and the second tube (71) can be easily and firmly fixed.

  According to a fourth aspect of the present invention, in the heat exchanger according to any one of the first to third aspects, the first fluid and the second heat exchange section (70) introduced into the first heat exchange section (60). ) Of the second fluid to be introduced into the first tube (61) and the second tube (71) of the second fluid to be introduced into the second fluid introduced into 1. The upstream side of the second turn part (61e, 71e) is the high temperature side tube upstream part, and the first side of the high temperature side tube through which the high temperature side fluid flows out of the first tube (61) and the second tube (71). 1. When the downstream side of the second turn part (61e, 71e) is the high temperature side tube downstream part, the temperature of the third fluid is lower than the temperature of the high temperature side fluid, and among the plurality of high temperature side tubes, At least some of the upstream side of the high temperature side tube Against temperature side tube downstream portion, characterized in that it is arranged in the flow direction upstream of the third fluid.

  According to this, on the upstream side of the fluid flow in the high temperature side tube, it is possible to secure a temperature difference between the high temperature side fluid and the third fluid and increase the heat radiation amount. As a result, since the temperature difference between the first fluid and the second fluid can be reduced, the difference in the amount of thermal strain between the first tube (61) and the second tube (71) can be alleviated, and heat exchange can be achieved. Damage to the vessel can be suppressed.

  According to a fifth aspect of the present invention, in the heat exchanger according to the fourth aspect, the first fluid introduced into the first heat exchange section (60) and the second fluid introduced into the second heat exchange section (70). Among the fluids, the lower temperature fluid is used as the low temperature side fluid, and the first and second turn parts (of the low temperature side tube through which the low temperature side fluid flows out of the first tube (61) and the second tube (71) ( 61e, 71e) are upstream of the low temperature side tube, and of the first tube (61) and the second tube (71), the first and second turn portions of the low temperature side tube through which the low temperature side fluid flows ( 61e, 71e), the temperature of the third fluid is lower than that of the low temperature side fluid when the downstream side of the low temperature side tube is the downstream side, and the plurality of first tubes (61) and the plurality of second tubes ( 71) of which the low temperature side fluid circulates Among the low temperature-side tube, the low-temperature side tube upstream portion of at least a portion, characterized in that with respect to the low temperature side tube downstream portion, is arranged in the flow direction upstream of the third fluid.

  According to this, on the upstream side of the fluid flow in the low temperature side tube, it is possible to secure a temperature difference between the low temperature side fluid and the third fluid and increase the heat radiation amount. As a result, since the temperature difference between the first fluid and the second fluid can be reduced, the difference in the amount of thermal strain between the first tube (61) and the second tube (71) can be alleviated, and heat exchange can be achieved. Damage to the vessel can be suppressed.

  According to a sixth aspect of the present invention, in the heat exchanger according to any one of the first to fourth aspects, the temperature of the third fluid is the first fluid introduced into the first heat exchange section (60) and Of the second fluid introduced into the second heat exchange section (70), the temperature is lower than the temperature of the fluid having the higher temperature and higher than the temperature of the fluid having the lower temperature. To do.

  According to this, in the heat exchanger (16), the temperature of the fluid on the high temperature side of the first fluid and the second fluid is decreased and the temperature of the fluid on the low temperature side is increased. The temperature difference between the two fluids can be reduced. As a result, the difference in the amount of thermal strain between the tubes (61, 71) can be alleviated, and damage to the heat exchanger (16) can be effectively suppressed.

  According to a seventh aspect of the present invention, in the heat exchanger according to any one of the first to third aspects, an upstream side of the first turn portion (61e) of the first tube (61) is located upstream of the first tube. A first tube downstream portion (612) on the downstream side of the first turn portion (61e) of the first tube (61), and a second turn portion (71e) of the second tube (71). ) Is the second tube upstream portion (711) and the second tube downstream portion (71e) of the second tube (71) is the second tube downstream portion (712). The tube upstream portion (611) and the second tube upstream portion (711) are arranged in the stacking direction of the first and second tubes (61, 71), and the first tube downstream portion (612) and the second tube The downstream part (712) is the first Characterized in that it is arranged side by side in the laminating direction of the second tube (61, 71).

  According to this, the temperature difference between the first fluid flowing through the first tube (61) and the second fluid flowing through the second tube (71) is reduced, and the first tube (61) and the second tube ( 71) can be reduced. The reason will be described in an embodiment described later.

  In the invention according to claim 8, in the heat exchanger according to claim 7, the first tube upstream portion (611) and the second tube upstream portion (711) are the first tube downstream portion (612) and the second tube upstream portion. It arrange | positions with respect to the tube downstream part (712) at the flow direction upstream of the 3rd fluid, It is characterized by the above-mentioned.

  According to this, when both the first fluid introduced into the first heat exchange unit (60) and the second fluid introduced into the second heat exchange unit (70) are higher in temperature than the third fluid, The temperature difference between the first fluid and the third fluid, and the temperature difference between the second fluid and the third fluid on the fluid flow upstream side of the first tube (611) and the fluid flow upstream side of the second tube (622). The amount of heat radiation can be increased by securing. As a result, the difference in the amount of thermal strain between the first tube (61) and the second tube (71) can be alleviated, and damage to the heat exchanger can be suppressed.

  According to a ninth aspect of the present invention, in the heat exchanger according to the seventh aspect, the plurality of first tubes (61) are upstream of the first fluid introduced into the first heat exchange section (60). The first tube group (60a) and the downstream first tube group (60b) through which the first fluid flowing out from the first heat exchange section (60) flows out from the upstream first tube group (60a). The plurality of second tubes (71) include an upstream second tube group (70a) through which a second fluid introduced into the second heat exchange section (70) flows, and an upstream second tube group (70a). ) And the downstream second tube group (70b) through which the second fluid flowing out from the second heat exchange section (70) flows, the upstream first tube group (60a) and the upstream second tube. The first tube upstream portion (611) and the tube group (60a) Second tube upstream portion (711), the first tube downstream portion (612) and the second tube downstream portion with respect to (712), characterized in that it is arranged in the flow direction upstream of the third fluid.

  According to this, when the temperature of both the first fluid introduced into the first heat exchange section (60) and the second fluid introduced into the second heat exchange section (70) is higher than that of the third fluid. The first fluid and the third fluid while reducing the temperature difference between the first fluid and the second fluid on the upstream side of the fluid flow of the upstream first tube group (60a) and the upstream second tube group (70a). And the temperature difference between the second fluid and the third fluid can be secured to increase the heat radiation amount. As a result, the difference in the amount of thermal strain between the first tube (61) and the second tube (71) can be alleviated, and damage to the heat exchanger can be suppressed.

  According to a tenth aspect of the present invention, in the heat exchanger according to the ninth aspect, the first tube upstream portion (611) and the first downstream tube group (60b) and the downstream second tube group (70b). The two-tube upstream portion (711) is disposed downstream of the first tube downstream portion (612) and the second tube downstream portion (712) in the third fluid flow direction.

  According to this, when the temperature of both the first fluid introduced into the first heat exchange section (60) and the second fluid introduced into the second heat exchange section (70) is higher than that of the third fluid. The amount of heat of the first fluid and the second fluid can be sufficiently dissipated to the third fluid on the downstream side of the fluid flow in the downstream first tube group (60b) and the downstream second tube group (70b). As a result, it is possible to improve the performance of the heat exchanger.

  According to an eleventh aspect of the present invention, in the heat exchanger according to any one of the first to tenth aspects, the outer fin (50) is joined to the first and second tubes (61, 71). A plurality of slits (50a) for locally weakening the rigidity are formed.

  According to this, when a difference in thermal strain occurs between the first tube (61) and the second tube (71), each tube (61, 71) is formed at each slit (50a) of the outer fin (50). It is possible to absorb the stress acting on the. Furthermore, by providing a plurality of slits (50a) in the outer fin (50), it is possible to suppress damage to the heat exchanger when a difference in the amount of thermal strain occurs in each tube (61, 71). Can do.

  In invention of Claim 12, in the heat exchanger as described in any one of Claim 1 thru | or 11, the refrigerant | coolant of the intermediate part of at least one of a 1st turn part (61e) and a 2nd turn part (71e) The passage area is formed to be larger than the fluid passage area of the fluid inflow portion and the fluid outflow portion.

  According to this, it is possible to reduce pressure loss when the first fluid passes through the first turn part (61e) or when the second fluid passes through the second turn part (71e).

  According to a thirteenth aspect of the present invention, in the heat exchanger according to any one of the first to twelfth aspects, at least one of the first tube (61) and the second tube (71) has an inner portion. Inner fins (65, 75) that promote heat exchange between the circulating refrigerant and the third fluid are arranged, and the end portions of the inner fins (65, 75) are the first turn portion (61e) or the second turn. It protrudes into the internal space of the part (71e).

  According to this, since the edge part of the inner fin (65, 75) protrudes into the internal space of the 1st turn part (61e) or the 2nd turn part (71e), the 1st tube (61) and the 2nd Bonding failure between the inner peripheral surface of the tube (71) and the inner fins (65, 75) can be suppressed.

  Specifically, in the heat exchanger according to any one of claims 1 to 13, as in the invention according to claim 14, the first tube (61) and the second tube (71) are: It may be composed of a plate tube formed by bonding a pair of plate-like members (61a, 61b, 71a, 71b), or as in the invention according to claim 15, the first tube (61) and The second tube (71) may be formed by bending a flat tube whose longitudinal cross section is formed into a flat shape.

  In addition, the code | symbol in the bracket | parenthesis of each means described in this column and the claim is an example which shows a corresponding relationship 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 lineblock diagram showing a refrigerant channel at the time of waste heat recovery operation of a heat pump cycle of a 1st embodiment. It is a whole block diagram which shows the refrigerant | coolant flow path etc. at the time of the cooling operation of the heat pump cycle of 1st Embodiment. It is an external appearance perspective view of the heat exchanger of 1st Embodiment. (A) is a front view of the refrigerant | coolant tube (cooling medium tube 71) of 1st Embodiment, (b) is a side view of (a). It is AA sectional drawing of FIG. It is BB sectional drawing of FIG. It is CC 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 a typical partial exploded perspective view in the heat exchanger of a 1st embodiment. It is an external appearance perspective view of the heat exchanger of 2nd Embodiment. It is a typical perspective view explaining the flow of the refrigerant and cooling water in the heat exchanger of a 2nd embodiment. It is a typical partial exploded perspective view in the heat exchanger of a 2nd embodiment. (A) is a front view of the refrigerant | coolant tube (cooling medium tube 71) of 3rd Embodiment, (b) is a side view of (a). It is a whole block diagram which shows the refrigerant | coolant flow path etc. at the time of the waste heat recovery driving | operation of the heat pump cycle of 4th Embodiment. It is a typical external appearance perspective view of the heat exchanger of 5th Embodiment. It is a typical external appearance perspective view explaining the flow of the refrigerant and cooling water in the heat exchanger of a 5th embodiment. It is typical sectional drawing of the header tank longitudinal direction of the heat exchanger of other embodiment. It is explanatory drawing for demonstrating the influence on the temperature difference of the refrigerant | coolant and cooling water in each tube by the difference in the structure of a heat exchanger. It is a typical fragmentary perspective view of the heat exchanger which concerns on other embodiment. It is explanatory drawing for demonstrating the outer fin which concerns on other embodiment.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings. In the following embodiments, the same or equivalent parts are denoted by the same reference numerals in the drawings.

(First embodiment)
A first embodiment of the present invention will be described with reference to FIGS. In this embodiment, the heat exchanger 16 of the present invention is applied to the heat pump cycle 10 that adjusts the temperature of the air blown into the vehicle interior in the vehicle air conditioner 1. FIGS. 1-4 is a whole block diagram of the vehicle air conditioner 1 of this embodiment. The vehicle air conditioner 1 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 vehicle interior air that is blown into the vehicle interior that is the air-conditioning target space. In other words, the heat pump cycle 10 switches the refrigerant flow path, heats the vehicle interior blown air that is the heat exchange target fluid to heat the vehicle interior, and cools the vehicle interior blown air to the vehicle. A cooling operation (cooling operation) for cooling the room can be executed.

  Further, in the heat pump cycle 10, the refrigerant reaches the outdoor heat exchanger 60 of the heat exchanger 16 during heating operation by changing the flow rate of the refrigerant, cooling water, and outside air flowing through the heat exchanger 16 as described later. It is also possible to execute a waste heat recovery operation in which the refrigerant absorbs the amount of heat of the traveling electric motor MG as an external heat source at the time of defrosting operation for removing frost by melting and heating operation. In addition, in the whole block diagram shown to the heat pump cycle 10 of FIGS. 1-4, the flow of the refrigerant | coolant at the time of each operation | movement is shown with the solid line arrow.

  Moreover, in the heat pump cycle 10 of this embodiment, the normal CFC-type refrigerant | coolant is employ | adopted as a refrigerant | coolant, and the subcritical refrigeration cycle in which the high pressure side refrigerant | coolant pressure does not exceed the critical pressure of a refrigerant | coolant is comprised. This refrigerant is mixed with refrigerating machine oil for lubricating the compressor 11, and a part of the refrigerating machine oil circulates in the cycle together with the refrigerant.

  First, the compressor 11 is disposed in the engine room, sucks the refrigerant in the heat pump cycle 10 and compresses and discharges the refrigerant. A fixed capacity compressor 11a having a fixed discharge capacity is fixed by the electric motor 11b. It is an electric compressor to drive. 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 this rotation speed control. Therefore, in the present embodiment, the electric motor 11b constitutes the discharge capacity changing means of the compressor 11.

  The refrigerant outlet of the compressor 11 is connected to the refrigerant inlet side of the indoor condenser 12 as a use side heat exchanger. The indoor condenser 12 is disposed in the casing 31 of the indoor air conditioning unit 30 of the vehicle air conditioner 1 and heats the high-temperature and high-pressure refrigerant that circulates inside the vehicle and the air blown into the vehicle interior after passing through the indoor evaporator 20 described later. It is a heat exchanger for heating to be exchanged. 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 60 of the composite heat exchanger 16 is connected to the outlet side of the heating fixed throttle 13.

  Further, on the refrigerant outlet side of the indoor condenser 12, a fixed throttle bypass passage that guides the refrigerant flowing out of the indoor condenser 12 to the outdoor heat exchanger 60 side of the heat exchanger 16 by bypassing the heating fixed throttle 13. 14 is connected. 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. Therefore, the refrigerant flowing out of the indoor condenser 12 flows into the outdoor heat exchange section 60 of the heat exchanger 16 through the fixed throttle bypass passage 14 side when the on-off valve 15a is open, and the on-off valve 15a When it is closed, it flows into the outdoor heat exchange section 60 of the 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 heat exchanger 16 is disposed in the engine room, and the outdoor heat exchanging unit 60 of the heat exchanger 16 has a function of exchanging heat between the low-pressure refrigerant flowing through the inside and the outside air blown from the blower fan 17. It is the heat exchange part which fulfills. Further, the outdoor heat exchanging unit 60 functions as an evaporating heat exchanging unit that evaporates the low-pressure refrigerant and exerts an endothermic effect during the heating operation, and functions as a heat dissipating heat exchanging unit that radiates the high-pressure refrigerant during the cooling operation. .

  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. Further, in the heat exchanger 16 of the present embodiment, the outdoor heat exchange unit 60 and the cooling water that circulates through the cooling water circulation circuit 40 and cools the traveling electric motor MG, and the outside air blown from the blower fan 17 and The radiator unit 70 that exchanges heat is integrally configured.

  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 60 and the radiator unit 70 of the heat exchanger 16. The detailed configuration of the composite heat exchanger 16 in which the cooling water circulation circuit 40, the outdoor heat exchange unit 60, and the radiator unit 70 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 60 of the heat exchanger 16. 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 path switching unit 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 60 and an inlet side of an accumulator 18 (to be described later) during heating operation, and during the cooling operation, The refrigerant flow path is switched to connect the outlet side and the inlet side of the cooling fixed throttle 19. The cooling fixed throttle 19 is a pressure reducing means for cooling operation that decompresses and expands the refrigerant that has flowed out of the outdoor heat exchanger 60 during the cooling operation, and the basic configuration thereof is the same as that of the heating fixed throttle 13.

  The refrigerant inlet side of the indoor evaporator 20 is connected to the outlet side of the cooling fixed throttle 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 air blown into the vehicle interior, It is a heat exchanger for cooling which cools vehicle interior blowing air.

  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. Therefore, the accumulator 18 functions to prevent the liquid phase refrigerant from being sucked into the compressor 11 and prevent liquid compression of 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 vehicle interior 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 that switches and introduces vehicle interior air (inside air) and outside air is disposed on the most upstream side of the air flow inside 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 air blown into the vehicle interior. In other words, the indoor evaporator 20 is arranged on the upstream side of the air flow of the vehicle interior blown air with respect to the indoor condenser 12.

  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 a heat exchange amount adjusting means for adjusting the heat exchange amount between the refrigerant discharged from the compressor 11 and the air blown into the passenger compartment in the indoor condenser 12 constituting the use side heat exchanger. . 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 is provided with cooling water (for example, ethylene glycol) as a cooling medium (heat medium) in a cooling water passage formed inside a traveling electric motor MG that is one of in-vehicle devices that generate heat during operation. This is a cooling medium circulation circuit that circulates the 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 70 of the composite heat exchanger 16, a bypass passage 44 for bypassing the radiator 70 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 unit 70 to allow cooling water to flow into the radiator unit 70, and the inlet side of the cooling water pump 41 and the bypass passage 44. The cooling medium circuit for switching the coolant to flow around the radiator unit 70 is switched. The operation of the three-way valve 42 is controlled by a control voltage output from the air conditioning control device, and constitutes a circuit switching means for the cooling medium circuit.

  That is, in the cooling water circulation circuit 40 of the present embodiment, as shown by the broken line arrows in FIG. 1 and the like, the cooling water is circulated in the order of the cooling water pump 41 → the traveling electric motor MG → the bypass passage 44 → the cooling water pump 41. The medium circuit and the cooling medium circuit that circulates the cooling water in the order of the cooling water pump 41 → the electric motor MG for traveling → the radiator unit 70 → the cooling water pump 41 can be switched as shown by the broken line arrows in FIG. .

  Therefore, when the three-way valve 42 switches to the cooling medium circuit that flows the cooling water around the radiator unit 70 while the electric motor MG for traveling is operating, the temperature of the cooling water does not radiate at the radiator unit 70 and To raise. That is, when the three-way valve 42 switches to the cooling medium circuit that flows the cooling water around the radiator unit 70, the amount of heat (heat generation amount) of the traveling electric motor MG is stored in the cooling water. .

  Further, when the three-way valve 42 switches to the cooling medium circuit that allows the cooling water to flow through the radiator unit 70 during the operation of the electric motor MG for traveling, the cooling water flows into the radiator unit 70 and flows from the blower fan 17. Exchanges heat with the blown outside air. Furthermore, in the heat exchanger 16 of the present embodiment, the cooling water flowing into the radiator unit 70 can exchange heat not only with the outside air but also with the refrigerant flowing through the outdoor heat exchange unit 60.

  Next, the detailed configuration of the composite heat exchanger 16 of the present embodiment will be described with reference to FIGS. FIG. 5 is an external perspective view of the heat exchanger 16 of the present embodiment, and FIG. 6A is a front view of the refrigerant tube 61 (cooling medium tube 71) of the outdoor heat exchange unit 60 (radiator unit 70). It is a figure, (b) is a side view of (a). 7 is an enlarged AA sectional view of FIG. 6A, FIG. 8 is an enlarged BB sectional view of FIG. 6A, and FIG. 9 is an enlarged sectional view of FIG. It is expanded CC sectional drawing. Further, FIG. 10 is a schematic perspective view for explaining the refrigerant flow and the cooling water flow in the heat exchanger 16.

  First, as shown in FIG. 5, the outdoor heat exchange unit 60 and the radiator unit 70 of the heat exchanger 16 include a plurality of tubes (61, 71) through which refrigerant or cooling water flows, and the lengths of the plurality of tubes. A so-called tank-and-tube type heat exchanger structure having a collecting / distributing tank (62, 72) or the like for collecting or distributing refrigerant or cooling water flowing through each tube is disposed on the direction end side. Has been.

  Specifically, the outdoor heat exchanging unit 60 extends in the stacking direction of the plurality of refrigerant tubes 61 through which the refrigerant as the first fluid flows and the plurality of refrigerant tubes 61 circulates through the refrigerant tubes 61. The refrigerant side header tank section 62 that collects or distributes the refrigerant to be circulated and the refrigerant as the third fluid flowing around the refrigerant tube 61 and the refrigerant tube 61 (outside air blown from the blower fan 17) ).

  On the other hand, the radiator unit 70 includes a plurality of cooling medium tubes 71 through which cooling water as the second fluid flows, and cooling water that extends in the stacking direction of the cooling medium tubes 71 and flows through the cooling medium tubes 71. It has a cooling medium side header tank section 72 for collecting or distributing, and heats the cooling water flowing through the cooling medium tube 71 and the air flowing around the cooling medium tube 71 (outside air blown from the blower fan 17). It is a heat exchange part to be exchanged.

  Moreover, in this embodiment, as these refrigerant | coolant tube 61 and cooling medium tube 71, as shown in FIG. 6, a pair of plate-shaped member 61a, 61b (71a, 71b) by which the uneven | corrugated | grooved part was provided in the plate surface is shown. ) The so-called plate tube formed by joining together in the middle is adopted. The plate-like members 61a and 61b (71a and 71b) are formed of a metal having excellent heat conductivity (in this embodiment, an aluminum alloy).

  Since the basic configuration of the refrigerant tube 61 and the cooling medium tube 71 of the present embodiment is the same, FIG. 6 illustrates the refrigerant tube 61 and the cooling medium corresponding to the components of the refrigerant tube 61. The reference numerals of the components of the tube 71 are shown in parentheses.

  Further, as shown in FIG. 5, the refrigerant tube 61 and the cooling medium tube 71 extend in a direction connecting a refrigerant side header tank part 62 and a cooling medium side header tank part 72, which will be described later, and the refrigerant side header tank It is arranged between the part 62 and the cooling medium side header tank part 72. In other words, the refrigerant side header tank part 62 is arranged on one end side in the longitudinal direction of the refrigerant tube 61 and the cooling medium tube 71, and the cooling medium side header tank part 72 is composed of the refrigerant tube 61 and the cooling medium tube. 71 is disposed on the other end side in the longitudinal direction.

  Each of the refrigerant tube 61 and the cooling medium tube 71 has one end in the longitudinal direction fixed to the refrigerant side header tank 62 and the other end in the longitudinal direction fixed to the cooling medium side header tank 72. Yes.

  As shown in FIG. 6, the refrigerant tube 61 extends in the longitudinal direction of the refrigerant tube 61 (a direction orthogonal to the flow direction of the outside air blown from the blower fan 17), and as shown in the sectional view of FIG. 7. In addition, the refrigerant flow paths 61 c having a flat cross-sectional shape are arranged in two rows along the flow direction X of the outside air blown from the blower fan 17. Therefore, a flat surface 61d that extends in parallel with the flow direction of the outside air blown from the blower fan 17 is formed on the outer surface of the portion of the refrigerant tube 61 that forms the refrigerant flow path 61c.

  Furthermore, as shown in the cross-sectional view of FIG. 8, the ends of the refrigerant side header tank portions 62 of both refrigerant flow paths 61 c provided in two rows open to the outside at the end of the refrigerant tube 61. ing. In the present embodiment, the refrigerant-side header tank 62 is disposed at the opening end of the refrigerant flow path 61c, so that the internal space of the refrigerant-side header tank 62 and both refrigerant flow paths 61c are communicated with each other. ing.

  On the other hand, as shown in the cross-sectional view of FIG. 9, the end portions on the side of the cooling medium side header tank 72 of the refrigerant flow paths 61 c arranged in two rows do not open to the outside of the refrigerant tube 61. Two rows of refrigerant flow paths 61c are connected to each other by a refrigerant side turn portion 61e. Thereby, the internal space of the cooling medium side header tank portion 72 and the refrigerant tube 61 do not communicate with each other, and the two rows of refrigerant flow paths 61c communicate with each other.

  Therefore, in the refrigerant tube 61 of the present embodiment, the refrigerant side turn part 61e is positioned closer to the cooling medium side header tank part 72 than the refrigerant side header tank part 62, and as shown by the solid line arrow in FIG. The refrigerant that has flowed from the refrigerant-side header tank 62 into one refrigerant flow path 61c arranged in two rows changes its flow direction at the refrigerant-side turn section 61e and flows into the other refrigerant flow path 61c. Return to the refrigerant side header tank 62.

  Moreover, the refrigerant passage area of the refrigerant | coolant side turn part 61e is formed larger than the refrigerant passage area of the refrigerant flow path 61c. That is, the refrigerant passage area of the intermediate part of the refrigerant side turn part 61e is formed larger than the refrigerant passage areas of the refrigerant inflow part and the refrigerant outflow part connected to the refrigerant flow path 61c in the refrigerant side turn part 61e. The refrigerant passage area is defined by a cross-sectional area perpendicular to the refrigerant flow direction.

  Further, an enlarged portion 61f that enlarges the refrigerant passage area of the refrigerant flow path 61c is provided on the opposite side of the refrigerant side turn portion 61e in the end portion of the refrigerant flow path 61c of the refrigerant tube 61, and this enlarged portion. The internal space of the refrigerant side header tank 62 and both refrigerant flow paths 61c communicate with each other through 61f. The enlarged portion 61f is formed to increase the internal surface area of the refrigerant tube 61 and improve pressure resistance.

  Further, an inner fin 65 that promotes heat exchange between the refrigerant and the outside air blown from the blower fan 17 is disposed in the refrigerant flow path 61 c of the refrigerant tube 61. The inner fin 65 is formed by bending a thin plate-like metal into a wave shape, and the longitudinal end portions of the inner fin 65 are, as shown in FIGS. 8 and 9, respectively, an enlarged portion 61f and a refrigerant side turn portion 61e. It protrudes into the internal space.

  As for the cooling medium tube 71, similarly to the refrigerant tube 61, the cooling medium flow path 71 c formed in a flat cross section has two rows along the flow direction X of the outside air blown from the blower fan 17. A flat surface 71d that extends in parallel to the flow direction of the outside air blown from the blower fan 17 is formed on the outer surface side of the portion of the cooling medium tube 71 that forms the cooling medium flow path 71c. ing.

  Further, the cooling medium flow path 71c of the cooling medium tube 71 communicates with the internal space of the cooling medium side header tank section 72 at the end on the cooling medium side header tank section 72 side. The end of 71c on the refrigerant side header tank 62 side is connected by a cooling medium side turn part 71e having the same configuration as that of the refrigerant side turn part 61e.

  Therefore, in the cooling medium tube 71, the cooling medium side turn part 71e is positioned closer to the refrigerant side header tank part 62 than the cooling medium side header tank part 72, and as shown by the broken line arrow in FIG. The refrigerant flowing into one cooling medium flow path 71c arranged in two rows from the cooling medium side header tank part 72 changes its flow direction at the cooling medium side turn part 71e to change the other cooling medium flow path. It flows into 71c and returns to the cooling medium side header tank part 72.

  An inner fin 75 that promotes heat exchange between the cooling water and the outside air blown from the blower fan 17 is disposed in the cooling medium flow path 71 c of the cooling medium tube 71. The inner fin 75 has the same configuration as the inner fin 65 disposed in the refrigerant flow path 61c, and the end portion in the longitudinal direction of the inner fin 75 protrudes into the internal space of the cooling medium side turn portion 71e and the enlarged portion 71f, respectively. ing.

  Further, the refrigerant tubes 61 and the cooling medium tubes 71 are alternately arranged in layers with their flat surfaces 61d and 71d being parallel to each other at predetermined intervals. That is, the refrigerant tube 61 is disposed between the cooling medium tubes 71, and conversely, the cooling medium tube 71 is disposed between the refrigerant tubes 61.

  The space formed between the refrigerant tube 61 and the cooling medium tube 71 forms an outside air passage 16a (third fluid passage) through which the outside air blown by the blower fan 17 flows.

  Further, in the outdoor air passage 16a, heat exchange between the refrigerant and the outside air in the outdoor heat exchange unit 60 and heat exchange between the cooling water and the outside air in the radiator unit 70 are promoted, and the refrigerant and the cooling medium flowing through the refrigerant tube 61 are promoted. The outer fin 50 that enables heat transfer between the cooling water flowing through the tube 71 for cooling is arranged in a state where the outer fin 50 is joined to the flat surface 61d of the refrigerant tube 61 and the flat surface 71d of the cooling medium tube 71 facing each other. Has been.

  As this outer fin 50, a corrugated fin obtained by bending a thin plate metal into a wave shape is adopted. In this embodiment, the outer fin 50 is joined to both the refrigerant tube 61 and the cooling medium tube 71. As a result, heat transfer between the refrigerant tube 61 and the cooling medium tube 71 is enabled.

  Next, detailed configurations of the refrigerant tube 61 and the cooling medium tube 71, and the refrigerant side header tank unit 62 and the cooling medium side header tank unit 72 will be described with reference to FIG. FIG. 11 is a schematic partially exploded perspective view of the heat exchanger 16. In FIG. 11, the outer fin 50 is not shown for clarity of illustration.

  As shown in FIG. 11, in the refrigerant tube 61, the upstream portion of the refrigerant-side turn portion 61e constitutes the refrigerant tube upstream portion 611, and the downstream portion of the refrigerant-side turn portion 61e constitutes the refrigerant tube downstream portion 612. It is composed. That is, the refrigerant tube 61 of the present embodiment includes the refrigerant tube upstream portion 611, the refrigerant side turn portion 61e, and the refrigerant tube downstream portion 612. In the refrigerant tube 61 of the present embodiment, the refrigerant tube upstream portion 611 is disposed downstream of the refrigerant tube downstream portion 612 in the outside air flow direction X.

  On the other hand, in the cooling medium tube 71, the upstream part of the cooling medium side turn part 71e constitutes the cooling medium tube upstream part 711, and the downstream part of the cooling medium side turn part 71e constitutes the cooling medium tube downstream part 712. It is composed. That is, the cooling medium tube 71 of the present embodiment includes the cooling medium tube upstream portion 711, the cooling medium side turn portion 71e, and the cooling medium tube downstream portion 712. In the cooling medium tube 71 of the present embodiment, the cooling medium tube upstream portion 711 is disposed upstream of the cooling medium tube downstream portion 712 in the flow direction X of the outside air.

  The refrigerant tube 61 and the cooling medium tube 71 of the present embodiment are arranged such that the refrigerant tube upstream portion 611 and the cooling medium tube downstream portion 712 are arranged in the stacking direction of the tubes 61, 71, and the refrigerant tube. The downstream portion 612 and the cooling medium tube upstream portion 711 are arranged so as to be aligned in the stacking direction of the tubes 61 and 71.

  In such a configuration, the refrigerant flowing through the refrigerant tube 61 flows from the downstream side in the flow direction of the outside air to the upstream side, and the cooling water flowing through the cooling medium tube 71 flows downstream from the upstream side in the flow direction of the outside air. Will flow to the side. Therefore, in the refrigerant tube 61 and the cooling medium tube 71, the flow direction of the refrigerant flowing through the refrigerant tube 61 and the flow direction of the cooling water flowing through the cooling medium tube 71 are opposite in the flow direction X of the outside air. It is comprised so that it may become a direction.

  Next, the refrigerant side header tank part 62 and the cooling medium side header tank part 72 will be described. The basic configurations of the refrigerant side header tank part 62 and the cooling medium side header tank part 72 are the same, and the refrigerant side header tank part 62 has a refrigerant side plate to which both the refrigerant tube 61 and the cooling medium tube 71 are fixed. A member 63 and a refrigerant side tank member 64 fixed to the refrigerant side plate member 63 are provided.

  A portion of the refrigerant side plate member 63 corresponding to the refrigerant tube 61 is provided with a communication hole penetrating the front and back, and the refrigerant tube 61 passes through the communication hole. Thereby, the internal space of the refrigerant | coolant side header tank part 62 and the refrigerant | coolant flow path 61c of the tube 61 for refrigerant | coolants are connecting. In addition, the width dimension of the flow direction of the outside air of the site | part inserted in this communicating hole among the tubes 61 for refrigerant | coolants is formed shorter than the width dimension of the refrigerant flow path 61c.

  Similarly, a portion of the refrigerant side plate member 63 corresponding to the cooling medium tube 71 is provided with a communication hole penetrating the front and back, and the communication hole is blocked by inserting the cooling medium tube 71. ing. In addition, the width dimension of the flow direction of the outside air of the part inserted in this communicating hole among the tubes 71 for cooling media is formed shorter than the width dimension of the cooling medium flow path 71c.

  Furthermore, the refrigerant side plate member 63 is provided with a recess 63 a that partitions the space formed between the refrigerant side plate member 63 by being fixed to the refrigerant side tank member 64. The recessed portion 63 a is provided in the entire area in the longitudinal direction of the refrigerant side plate member 63.

  The refrigerant side tank member 64 is fixed to the refrigerant side plate member 63, thereby forming therein a collection space 62a for collecting refrigerant and a distribution space 62b for distributing refrigerant. Specifically, the refrigerant side tank member 64 is formed in a double mountain shape (W shape) when viewed from the longitudinal direction by pressing a flat metal.

  And the collective space 62a and the distribution space 62b are divided by joining the two mountain-shaped center part 64a of the refrigerant | coolant side tank member 64 to the recessed part 63a of the refrigerant | coolant side plate member 63. As shown in FIG. In the present embodiment, the collective space 62a is arranged on the leeward side in the flow direction X of the outside air, and the distribution space 62b is arranged on the leeward side in the flow direction X of the outside air.

  Further, as described above, the refrigerant tube 61 passes through the communication hole of the refrigerant side plate member 63, so that the refrigerant flow path 61c (refrigerant tube downstream portion 612) arranged on the windward side in the flow direction X of the outside air. ) Communicates with the collecting space 62a, and the refrigerant flow path 61c (refrigerant tube upstream portion 611) arranged on the leeward side in the flow direction X of the outside air communicates with the distribution space 62b.

  Further, as shown in FIG. 5, a refrigerant introduction pipe 64b for introducing the refrigerant into the distribution space 62b is connected to one end side in the longitudinal direction of the refrigerant side tank member 64, and the refrigerant is led out from the collective space 62a. A pipe 64c is connected. Further, the other end in the longitudinal direction of the refrigerant side tank member 64 is closed by a closing member.

  On the other hand, the cooling medium side header tank portion 72 also has a cooling medium side plate member 73 and a cooling medium side tank member 74 as shown in FIG. In the cooling medium side plate member 73, the cooling medium tube 71 passes through a communication hole provided in a portion corresponding to the cooling medium tube 71, and is provided in a portion corresponding to the refrigerant tube 61. The communication hole is closed by inserting the refrigerant tube 61.

  Further, the cooling medium side plate member 73 and the cooling medium side tank member 74 are fixed, and the concave portion 73a of the cooling medium side plate member 73 and the double mountain-shaped central portion 74a of the cooling medium side tank member 74 are joined. Thus, a collecting space 72a for collecting cooling water and a distribution space 72b for distributing cooling water are partitioned in the interior. In the present embodiment, the distribution space 72b is arranged on the leeward side in the flow direction X of the outside air, and the collective space 72a is arranged on the leeward side in the flow direction X of the outside air.

  As described above, the cooling medium tube 71 passes through the communication hole of the cooling medium side plate member 73, so that the cooling medium flow path 71c (cooling medium) arranged on the windward side in the flow direction X of the outside air. The tube upstream portion 711) communicates with the distribution space 72b, and the cooling medium flow channel 71c (cooling medium tube downstream portion 712) arranged on the leeward side in the flow direction X of the outside air communicates with the collective space 72a.

  Further, as shown in FIG. 5, a cooling medium introduction pipe 74b for introducing the cooling medium into the distribution space 72b is connected to one end side in the longitudinal direction of the cooling medium side tank member 74, and the cooling medium is supplied from the collective space 72a. A cooling medium outlet piping 74c to be led out is connected. Further, the other end in the longitudinal direction of the cooling medium side header tank portion 72 is closed by a closing member.

  Therefore, in the heat exchanger 16 of the present embodiment, as shown in the schematic perspective view of FIG. 10, the refrigerant introduced into the distribution space 62b of the refrigerant side header tank portion 62 via the refrigerant introduction pipe 64b is 2 Of the refrigerant tubes 61 arranged in a row, the refrigerant flows into the refrigerant flow path 61c (refrigerant tube upstream portion 611) of the refrigerant tubes 61 arranged on the leeward side in the flow direction X of the outside air.

  Then, the refrigerant flowing out from the refrigerant flow path 61c (refrigerant tube upstream portion 611) arranged on the leeward side passes through the refrigerant side turn portion 61e, and the refrigerant flow path 61c (refrigerant tube downstream portion 612) arranged on the leeward side. ). Furthermore, the refrigerant that has flowed out of the refrigerant flow path 61c (refrigerant tube downstream portion 612) arranged on the windward side gathers in the collecting space 62a of the refrigerant side header tank portion 62 and is led out from the refrigerant outlet pipe 64c.

  That is, in the heat exchanger 16 of the present embodiment, the refrigerant is a refrigerant channel 61c on the leeward side of the refrigerant tube 61 (refrigerant tube upstream portion 611) → refrigerant-side turn portion 61e → refrigerant on the windward side of the refrigerant tube 61. It flows while making a U-turn in the order of the flow path 61c (refrigerant tube downstream portion 612).

  Similarly, with respect to the cooling water, the cooling medium flow path 71c on the windward side of the cooling medium tube 71 (cooling medium tube upstream part 711) → the cooling medium side turn part 71e → the cooling medium flow on the leeward side of the cooling medium tube 71. It flows while making a U-turn in the order of the path 71c (cooling medium tube downstream portion 712). Accordingly, the refrigerant flowing through the adjacent refrigerant tubes 61 and the cooling water flowing through the cooling medium tubes 71 are opposed to each other in the longitudinal direction of the tubes 61 and 71 and in the flow direction of the outside air. Direction (counterflow structure).

  The inner fins 65 and 72, the constituent parts of the refrigerant-side header tank section 62, the constituent parts of the cooling medium-side header tank section 72, and the outer fin 50 are all refrigerant tubes 61 and cooling medium tubes 71. Are formed of the same metal material as the plate-like members 61a, 61b, 71a, 71b.

  Next, the manufacturing method of this heat exchanger 16 is demonstrated. First, the refrigerant tube 61 and the cooling medium tube 71, and the refrigerant side header tank part 62 and the cooling medium side header tank part 72 are temporarily fixed (tube / tank temporary fixing process).

  Specifically, with respect to the refrigerant tube 61, the plate-like members 61a and 61b are combined in the middle with the inner fins 65 fitted into the portions corresponding to the refrigerant flow paths 61c, and the plate-like member 61a is combined. The claws formed on at least part of the upstream and downstream sides in the outside air flow direction (in the present embodiment, the entire area in the vertical direction) are bent toward the plate-like member 61b.

  Further, the plate-like member 61a of the present embodiment has claw portions 61g also formed between the refrigerant flow paths 61c arranged in two rows, and this claw portion is formed on the through hole side formed in the plate-like member 61b. Temporarily fixed by bending to the side. Similarly, the plate-like members 71a and 71b and the inner fins 75 are temporarily fixed for the cooling medium tube 71 as well.

  For the refrigerant-side header tank 62, the refrigerant-side plate member 63 and the refrigerant-side tank member 64 are combined, and the claw portion formed at the outer peripheral end of the refrigerant-side tank member 64 is bent toward the refrigerant-side plate member 63. It is temporarily fixed by. Similarly, the cooling medium side plate member 73 and the cooling medium side tank member 74 are also temporarily fixed to the cooling medium side header tank portion 72.

  The refrigerant tube 61 and the cooling medium tube 71, and the refrigerant side header tank part 62 and the cooling medium side header tank part 72 may be temporarily fixed in any order.

  Next, the refrigerant tube 61 and the cooling medium tube 71 are connected to the refrigerant side plate member 63 of the refrigerant side header tank portion 62 and the cooling medium side plate member 73 of the cooling medium side header tank portion 72, respectively. Insert into. At this time, in this embodiment, the distance from the opening edge portion of the communication hole to each turn portion 61e, 71e and each enlarged portion 61f, 71f is fitted and inserted so as to be 3 mm or less.

  Further, the outer fin 50 is fitted and temporarily fixed to the outside air passage 16a formed in the refrigerant tube 61 and the cooling medium tube 71, and the inlet / outlet pipes 64b, 64c, 74b, 74c, etc. are temporarily fixed (heat). Exchanger temporary fixing process).

  Then, after fixing the temporarily assembled heat exchanger 16 with a wire jig or the like, the entire heat exchanger 16 is put into a heating furnace and heated to melt the brazing material clad in advance on the surface of each component. Furthermore, by cooling until the brazing material is solidified again, the components are integrally brazed and joined (heat exchanger joining process). Thereby, the heat exchanger 16 in which the outdoor heat exchange unit 60 and the radiator unit 70 are integrated is manufactured.

  As is clear from the above description, the outdoor heat exchange unit 60 of the present embodiment corresponds to the first heat exchange unit described in the claims, and the refrigerant tube 61 corresponds to the first tube. The refrigerant side header tank part 62 corresponds to the first tank part, and the refrigerant side turn part 61e corresponds to the first turn part.

  The refrigerant tube upstream portion 611 of the cooling medium tube 61 corresponds to the first tube upstream portion described in the claims, and the refrigerant tube downstream portion 612 corresponds to the first tube downstream portion.

  On the other hand, the radiator section 70 corresponds to the second heat exchange section described in the claims, the cooling medium tube 71 corresponds to the second tube, and the cooling medium side header tank section 72 corresponds to the second tank section. Correspondingly, the coolant side turn part 71e corresponds to the second turn part.

  The cooling medium tube upstream portion 711 of the cooling medium tube 71 corresponds to the second tube upstream portion described in the claims, and the cooling medium tube downstream portion 712 corresponds to the second tube downstream portion. Yes.

  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 operation of various air conditioning control devices 11, 15a, 15b, 17, 41, 42, etc. is 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) Temperature)), an outlet refrigerant temperature sensor for detecting the refrigerant temperature discharged from the compressor 11, an outlet refrigerant temperature sensor 51 for detecting the refrigerant temperature Te on the outlet side of the outdoor heat exchanger 60, and an electric motor MG for running. Various air conditioning control sensors such as a cooling water temperature sensor 52 as a cooling water temperature detecting means for detecting the cooling water temperature Tw to be detected are connected.

  In the present embodiment, the coolant temperature sensor 52 detects the coolant temperature Tw pumped from the coolant pump 41. Of course, the coolant temperature Tw sucked into the coolant pump 41 is detected. Also good.

  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.

  Further, the air conditioning control device is configured integrally with control means for controlling the electric motor 11b of the compressor 11, the on-off valve 15a, etc., and controls these operations. In this embodiment, the air conditioning control device Among these, the configuration (hardware and software) for controlling the operation of the compressor 11 constitutes the refrigerant discharge capacity control means, and the configuration for controlling the operations of the various devices 15a and 15b constituting the refrigerant flow path switching means. The structure which comprises a control means and controls the action | operation of the three-way valve 42 which comprises the circuit switching means of a cooling water comprises the cooling medium circuit control means.

  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 60 based on the detection signal of the above-described air conditioning control sensor group (frosting determination means). have. Specifically, in the frost determination unit of the present embodiment, the vehicle speed of the vehicle is equal to or lower than a predetermined reference vehicle speed (20 km / h in the present embodiment), and the outdoor heat exchanger 60 outlet side refrigerant temperature is When Te is 0 ° C. or lower, it is determined that frost formation has occurred in the outdoor heat exchange unit 60.

  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 and a waste heat recovery operation are performed during the heating operation. Can do. 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. During the heating operation, when it is determined by the frost determination means that frost formation has occurred in the outdoor heat exchanger 60, the defrost operation is performed, and the cooling water temperature Tw detected by the cooling water temperature sensor 52 is detected. When the temperature reaches or exceeds a predetermined reference temperature (60 ° C. in this embodiment), the waste heat recovery operation is executed.

  First, during normal heating operation, the air conditioning control device 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 60 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 medium circuit in which the cooling water flows around the radiator unit 70.

  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 switched to the cooling medium circuit through which the refrigerant flows as shown by the broken line arrows in FIG. It is done.

  With the configuration of the refrigerant flow path and the cooling medium circuit, the air conditioning control device reads the detection signal of the above-described sensor group for air conditioning control 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.

  During normal heating operation, defrosting operation, and waste heat recovery operation, the air mix door 34 is opened so that the total air volume of the vehicle interior air blown from the blower 32 passes through the indoor condenser 12. The degree may be controlled.

  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 vehicle interior blown air that has been blown from the blower 32 and passed through the indoor evaporator 20 to dissipate heat. Thereby, vehicle interior 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. Then, the low-pressure refrigerant decompressed and expanded by the heating fixed throttle 13 flows into the outdoor heat exchange unit 60. The low-pressure refrigerant that has flowed into the outdoor heat exchange unit 60 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 medium circuit that flows around the radiator unit 70, the cooling water radiates heat to the refrigerant circulating in the outdoor heat exchange unit 60, and the cooling water Does not absorb heat from the refrigerant flowing through the outdoor heat exchanger 60. That is, the cooling water does not thermally affect the refrigerant flowing through the outdoor heat exchange unit 60.

  The refrigerant flowing out of the outdoor heat exchange section 60 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 60 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 vehicle interior air can be heated by the amount of heat of the refrigerant discharged from the compressor 11 by the indoor condenser 12 to heat the vehicle interior.

(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 apparatus that evaporates the refrigerant by exchanging heat between the refrigerant and the outside air in the outdoor heat exchange unit 60, the refrigerant evaporation temperature in the outdoor heat exchange unit 60 reaches the temperature. If the temperature is lower than the frost temperature (specifically, 0 ° C.), the outdoor heat exchange unit 60 may be frosted.

  When such frost formation occurs, the outdoor air passage 16a of the heat exchanger 16 is blocked by frost, so that the heat exchange capability of the outdoor heat exchange unit 60 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 60 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. Therefore, during the defrosting operation, the flow rate of the refrigerant flowing into the outdoor heat exchange unit 60 is reduced and the air volume of the outside air flowing into the outdoor air passage 16a 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 medium circuit that allows the cooling water to flow into the radiator section 70 as indicated by the broken line arrows in FIG. As a result, the refrigerant does not circulate in the heat pump cycle 10, and the cooling water circulation circuit 40 is switched to the cooling medium circuit through which the refrigerant flows as shown by the broken line arrows in FIG.

  Accordingly, the heat quantity of the cooling water flowing through the cooling medium tube 71 of the radiator section 70 is transferred to the outdoor heat exchange section 60 through the outer fins 50, and the outdoor heat exchange section 60 is defrosted. That is, by changing (specifically, decreasing) the flow rate of the refrigerant and the outside air flowing through the heat exchanger 16, defrosting that effectively uses the waste heat of the traveling electric motor MG is realized.

(C) Waste heat recovery operation Next, the waste heat recovery operation will be described. Here, in order to suppress overheating of the traveling electric motor MG, the temperature of the cooling water is maintained at a predetermined upper limit temperature or less, and the viscosity of the lubricating oil enclosed in the traveling electric motor MG is increased. In order to reduce the friction loss due to the above, it is desirable that the temperature of the cooling water is maintained at a predetermined lower limit temperature or higher.

  Therefore, in the heat pump cycle 10 of the present embodiment, the waste heat recovery operation is executed when the cooling water temperature Tw becomes equal to or higher than a predetermined reference temperature (60 ° C. in the present embodiment) during the heating operation. In this defrosting operation, the three-way valve 15b of the heat pump cycle 10 is operated in the same manner as in normal heating operation, and the three-way valve 42 in the cooling water circulation circuit 40 is supplied with cooling water in the same manner as in the defrosting operation. 3 is switched to a cooling medium circuit that flows into the radiator section 70 as indicated by a broken line arrow 3.

  Therefore, as shown by the solid line arrows in FIG. 3, the high-pressure and high-temperature refrigerant discharged from the compressor 11 heats the air blown into the vehicle interior by the indoor condenser 12 in the same way as during normal heating operation, and fixed for heating. The throttle 13 is decompressed and expanded and flows into 16.

  The low-pressure refrigerant that has flowed into the outdoor heat exchanging unit 60 is switched to a cooling medium circuit in which the three-way valve 42 flows cooling water into the radiator unit 70, so that the amount of heat of the outside air blown by the blower fan 17 and the outer fin 50 are reduced. It absorbs both the heat quantity of the cooling water transferred through the heat and absorbs it to evaporate. Other 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 amount of heat of the refrigerant discharged from the compressor 11 by the indoor condenser 12, and the vehicle interior can be heated. At this time, the refrigerant absorbs not only the amount of heat that the outside air has but also the amount of cooling water that is transferred through the outer fins 50, so that the vehicle interior can be effectively heated by using the waste heat of the electric motor MG for traveling. realizable.

(D) Cooling operation Cooling operation is started when the operation switch of the operation panel is turned on (ON) and the cooling operation mode is selected by the selection switch. During this cooling operation, the air conditioning control device 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 60 and the inlet side of the cooling fixed throttle 19. 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.

  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 medium circuit that allows the cooling water to flow into the radiator unit 70. When the temperature becomes lower than the set reference temperature, the coolant is switched to a coolant medium circuit that flows around the radiator unit 70. In FIG. 4, 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 dashed 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 and exchanges heat with the vehicle interior blown air that is blown from the blower 32 and passes through the indoor evaporator 20. Dissipate heat. The high-pressure refrigerant that has flowed out of the indoor condenser 12 flows into the outdoor heat exchange section 60 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 60 further radiates heat to the outside air blown by the blower fan 17.

  The refrigerant that has flowed out of the outdoor heat exchange unit 60 is switched to a refrigerant flow path in which the three-way valve 15b connects the outlet side of the outdoor heat exchange unit 60 and the inlet side of the cooling fixed throttle 19, so that the cooling fixed The diaphragm 19 is expanded under reduced pressure. The refrigerant that has flowed out of the cooling fixed throttle 19 flows into the indoor evaporator 20, absorbs heat from the vehicle interior air blown by the blower 32, and evaporates. Thereby, vehicle interior 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 vehicle interior blown air and evaporates in the room evaporator 20, thereby cooling the vehicle interior blown air and cooling the vehicle interior.

  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 medium circuit of the cooling water circulation circuit 40 as described above. Furthermore, in this embodiment, since the characteristic heat exchanger 16 mentioned above is employ | adopted, appropriate heat exchange can be performed between three types of fluids, a refrigerant | coolant, cooling water, and external air at the time of an operation | movement, respectively.

  More specifically, in the heat exchanger 16 of the present embodiment, the outer fin 50 is provided in the outside air passage 16a formed between the refrigerant tube 61 of the outdoor heat exchange unit 60 and the cooling medium tube 71 of the radiator unit 70. It is arranged. The outer fin 50 enables heat transfer between the refrigerant tube 61 and the cooling medium tube 71.

  Thus, during the defrosting operation, the amount of heat of the cooling water can be transferred to the outdoor heat exchange unit 60 via the outer fin 50, so that the waste heat of the traveling electric motor MG is removed by the outdoor heat exchange unit 60. It can be used effectively due to frost.

  Further, in the present embodiment, during the defrosting operation, the operation of the compressor 11 is stopped and the refrigerant flow rate flowing into the outdoor heat exchange unit 60 is reduced, so that the outdoor air is passed through the outer fin 50 and the refrigerant tube 61. It can be suppressed that the amount of heat transferred to the heat exchange unit 60 is absorbed by the refrigerant flowing through the refrigerant tube 61. That is, unnecessary heat exchange between the cooling water and the refrigerant can be suppressed.

  Further, during the defrosting operation, the operation of the blower fan 17 is stopped to reduce the air volume of the outside air flowing into the outside air passage 16a, so that the amount of heat transferred to the outdoor heat exchanging unit 60 through the outer fin 50 is outside air. It is possible to suppress heat absorption by the outside air flowing through the passage 16a. That is, unnecessary heat exchange between the cooling water and the outside air can be suppressed.

  Further, during the waste heat recovery operation, heat is exchanged between the coolant and the refrigerant through the refrigerant tube 61, the cooling medium tube 71, and the outer fin 50, so that the waste heat of the traveling electric motor MG is absorbed by the refrigerant. In addition, it is possible to dissipate unnecessary waste heat from the traveling electric motor MG to the outside air by exchanging heat between the cooling water and the outside air via the cooling medium tubes 71 and the outer fins 50.

  Further, during normal heating operation, the refrigerant and the outside air can be heat-exchanged via the refrigerant tubes 61 and the outer fins 50, and the amount of heat of the outside air can be absorbed by the refrigerant. Furthermore, during normal heating operation, the three-way valve 42 of the cooling water circulation circuit 40 is switched to a cooling medium circuit in which the cooling water flows around the radiator unit 70, thereby suppressing heat exchange between unnecessary cooling water and outside air. Thus, the waste heat of the traveling electric motor MG can be stored in the cooling water, and warming up of the traveling electric motor MG can be promoted.

  Further, in the heat exchanger 16 of the present embodiment, the refrigerant tube 61 and the cooling medium tube 71 are disposed between the refrigerant side header tank unit 62 and the cooling medium side header tank unit 72, and the refrigerant tube 61 and the cooling medium tube 71 are cooled. Since the outside air passage 16a is formed by the space formed between the medium tube 71, the refrigerant side header tank part 62 and the cooling medium side header tank part 72 are not arranged side by side in the flow direction of the outside air. Therefore, the heat exchanger 16 as a whole can be prevented from being enlarged in the direction of the outside air flow.

  Moreover, the refrigerant side turn part 61e of the refrigerant tube 61 is positioned closer to the cooling medium side header tank part 72 than the refrigerant side header tank part 62, and the cooling medium side turn part 71e of the cooling medium tube 71 is positioned on the cooling medium side. Since it is positioned at a position closer to the refrigerant side header tank part 62 than the header tank part 72, the refrigerant tube 61 is connected to the refrigerant side header tank part 62, and the cooling medium side header tank part 72 is used for the cooling medium. The thing of the same shape as what connected the tube 71 is employable.

  In the present embodiment, the refrigerant side plate member 63 of the refrigerant side header tank unit 62 and the cooling medium side plate member 73 of the cooling medium side header tank unit 72 are communicated with the refrigerant channel 61c or the cooling medium channel 71c. Since the hole and the communication hole to be closed are provided, a refrigerant tube 61 is connected to the refrigerant header tank 62, and a cooling medium tube 71 is connected to the cooling medium header tank 72. Can have the same shape, and the productivity can be improved.

  As a result, according to the heat exchanger 16 of the present embodiment, it is possible to improve the productivity of a heat exchanger that can perform heat exchange between three types of fluids without causing an increase in size.

  Moreover, in the heat exchanger 16 of this embodiment, since the refrigerant | coolant tube 61 and the cooling medium tube 71 are all fixed to both the refrigerant | coolant side header tank part 62 and the cooling medium side header tank part 72, heat The mechanical strength of the exchanger 16 as a whole can be increased. Furthermore, when the outer fin 50 disposed in the outside air passage 16a is temporarily processed, it can be temporarily fixed extremely easily and can be firmly fixed after joining.

  Further, since the refrigerant passage area at the intermediate portion between the refrigerant side turn portion 61e and the cooling medium side turn portion 71e is formed larger than the fluid passage area of the fluid inflow portion and the fluid outflow portion, the refrigerant is the refrigerant side turn portion. Pressure loss when passing through 61e or when cooling water passes through the coolant side turn part 71e can be reduced.

  Further, the end portions of the inner fins 65 and 75 arranged inside the refrigerant tube 61 and the cooling medium tube 71 protrude into the internal spaces of the turn portions 61e and 71e and the enlarged portions 61f and 71f, respectively. The portions where the brazing agent clad such as the end portions of the inner fins 65 and 75 are easily peeled off are not the surfaces to be brazed, and the inner peripheral surfaces of the refrigerant tube 61 and the cooling medium tube 71 and the inner fins 65 and 75. It is easy to suppress bonding failure with.

  Here, as in the present embodiment, in the heat exchanger 16 capable of exchanging heat between three types of fluids, the temperature of the refrigerant introduced into the outdoor heat exchange unit 60 and the radiator unit 70 are introduced depending on the operating conditions. The cooling water temperature may be different. In this case, there is a concern that the heat exchanger 16 may be damaged because the amount of thermal strain (thermal expansion amount) generated in the refrigerant tube 61 and the cooling medium tube 71 is different.

  On the other hand, in the heat exchanger 16 of this embodiment, the structure which arrange | positions the outer fin 50 between the tube 61 for refrigerant | coolants and the tube 71 for cooling media alternately laminated | stacked and arrange | positioned at predetermined intervals. Since the heat exchange of the outside air, the refrigerant, and the cooling water is promoted by the outer fin 50, the difference in the amount of thermal strain between the tubes 61 and 71 can be alleviated. Therefore, in the heat exchanger 16 of the present embodiment, it is possible to suppress damage due to the difference in the amount of thermal strain (thermal expansion amount) generated in the refrigerant tube 61 and the cooling medium tube 71.

  Further, in the heat exchanger 16 of the present embodiment, the cooling medium tube upstream portion 711 of the cooling medium tube 71 is arranged upstream of the cooling medium tube downstream portion 712 in the flow direction X of the outside air. For this reason, for example, in an operation state in which the temperature of the cooling medium flowing into the cooling medium tube 71 is higher than the temperatures of the refrigerant and the outside air, the cooling water and the outside air are upstream of the cooling medium flow in the cooling medium tube 71. The amount of heat radiation can be increased by securing the temperature difference. As a result, the temperature difference between the cooling water and the refrigerant can be reduced, and the difference in thermal strain between the refrigerant tube 61 and the cooling medium tube 71 can be reduced. In this example, the cooling water corresponds to a “high temperature side fluid”, the cooling medium tube 71 constitutes a “high temperature side tube”, and the cooling medium tube upstream portion 711 of the cooling medium tube 71 is “high temperature side”. Further, the cooling medium tube downstream portion 712 of the cooling medium tube 71 forms a “high temperature side tube downstream portion”. Further, the refrigerant corresponds to the “low temperature side fluid”, the refrigerant tube 61 constitutes the “low temperature side tube”, the refrigerant tube upstream portion 611 of the refrigerant tube 61 constitutes the “low temperature side tube upstream portion”, Furthermore, the refrigerant tube downstream portion 612 of the refrigerant tube 61 constitutes a “low temperature side tube downstream portion”.

(Second Embodiment)
This embodiment demonstrates the example which changed the structure of the heat exchanger 16 with respect to 1st Embodiment. A detailed configuration of the heat exchanger 16 of the present embodiment will be described with reference to FIGS.

  12 is an external perspective view of the heat exchanger 16 of the present embodiment, FIG. 13 is a schematic perspective view for explaining the refrigerant flow and the cooling water flow of the heat exchanger 16, and FIG. FIG. 2 is a schematic partially exploded perspective view of the heat exchanger 16 and corresponds to FIGS. 5, 10, and 11 of the first embodiment, respectively. In FIGS. 12 to 14, 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.

  As shown in FIGS. 12 and 14, the refrigerant tube 61 and the cooling medium tube 71 of the present embodiment are formed by bending a flat tube whose longitudinal cross section is formed into a flat shape. More specifically, the refrigerant tube 61 is bent so that the flat surfaces thereof face each other, and the cooling medium tube 71 is bent so that the flat surfaces thereof face each other.

  Therefore, the refrigerant side turn portion 61e of the refrigerant tube 61 and the cooling medium side turn portion 71e of the cooling medium tube 71 of the present embodiment are formed by the bent portions of the tubes 61 and 71, respectively. Further, the outside air passage 16a of the present embodiment is not only between the flat surfaces of the opposing refrigerant tubes 61 and the cooling medium tube 71 but also between the flat surfaces of the refrigerant tubes 61 facing each other. It is also formed between the flat surfaces of the cooling medium tube 71.

  And the outer fin 50 similar to 1st Embodiment is arrange | positioned in these external air channel | paths 16a. In FIG. 14, as in FIG. 11, the outer fins 50 are not shown for clarity of illustration.

  Further, as shown in FIG. 14, the refrigerant tubes 61 are arranged in two rows along the flow direction X of the outside air, and one open end of the refrigerant tube 61 arranged on the leeward side is a refrigerant. One open end of the refrigerant tube 61 arranged on the windward side communicates with the distribution space 62 b of the side header tank 62 and communicates with the collective space 62 a of the refrigerant side header tank 62.

  Further, a partition member (not shown) is disposed inside the refrigerant side header tank 62, and the other opening end portions of the refrigerant tubes 61 disposed on the windward side and the leeward side are arranged by this partition member, The refrigerant side header tank portion 62 communicates with each other without communicating with the collective space 62a and the distribution space 62b.

  On the other hand, as shown in FIG. 14, the cooling medium tubes 71 are also arranged in two rows along the outside air flow direction X, and one open end of the cooling medium tubes 71 disposed on the windward side. Part communicates with the distribution space 72 b of the cooling medium side header tank part 72, and one open end of the cooling medium tube 71 arranged on the leeward side communicates with the collective space 72 a of the cooling medium side header tank part 72. Yes.

  Further, a partition member (not shown) is also arranged inside the cooling medium side header tank portion 72, and the other opening end portions of the cooling medium tubes 71 disposed on the windward side and the leeward side are arranged by this partition member. However, they communicate with each other without communicating with the collecting space 72a and the distribution space 72b inside the cooling medium side header tank portion 72.

  Therefore, in the heat exchanger 16 of the present embodiment, as shown in FIG. 13, the refrigerant introduced into the distribution space 62b of the refrigerant header tank 62 flows into the refrigerant tube 61 disposed on the leeward side, It passes through the refrigerant side turn part 61e of the refrigerant tube 61 arranged on the leeward side, returns to the refrigerant side header tank part 62, flows into the refrigerant tube 61 arranged on the windward side, and is arranged on the windward side. The refrigerant passes through the refrigerant side turn part 61 e of the refrigerant tube 61 and is led out from the collective space 62 a of the refrigerant side header tank part 62.

  On the other hand, the refrigerant introduced into the distribution space 72b of the cooling medium side header tank 72 flows into the cooling medium tube 71 disposed on the windward side, and the cooling medium side of the cooling medium tube 71 disposed on the windward side. It passes through the turn part 71e, returns to the cooling medium side header tank part 72, flows into the cooling medium tube 71 disposed on the leeward side, and cools the cooling medium side turn part of the cooling medium tube 71 disposed on the leeward side. It passes through 71e and is led out from the collective space 72a of the cooling medium side header tank 72.

  The configuration and operation of the heat pump cycle 10 including other heat exchangers 16 are the same as those in the first embodiment. Therefore, also in the heat exchanger 16 of the present embodiment, appropriate heat exchange can be performed between the three types of fluids of the refrigerant, the cooling water, and the outside air during the operation of the heat pump cycle 10 as in the first embodiment. In addition, the productivity of the heat exchanger capable of performing heat exchange between the three types of fluids can be improved without causing an increase in size.

  Further, in the heat exchanger 16 of the present embodiment, since the refrigerant tube 61 and the cooling medium tube 71 are flat tubes that can be formed at low cost by extrusion processing or drawing processing, etc., it is even more so. , Productivity can be improved.

(Third embodiment)
In the second embodiment, as the refrigerant tube 61 and the cooling medium tube 71, the example in which the flat tubes bent so that the flat surfaces are opposed to each other has been described, but in the present embodiment, as illustrated in FIG. 15. As described above, the upstream side flat surface and the downstream side flat surface of each turn part 61e, 71e are bent so as to be arranged in two rows on the same plane along the flow direction X of the outside air.

  FIG. 15A is a front view of the refrigerant tube 61 (cooling medium tube 71) of the present embodiment, and FIG. 15B is a side view of FIG. It is drawing corresponding to FIG. 6 (a), (b). Accordingly, in FIG. 15, the refrigerant tube 61 is illustrated, and the reference numerals of the components of the cooling medium tube 71 corresponding to the components of the refrigerant tube 61 are shown in parentheses.

  The configuration and operation of the heat pump cycle 10 including other heat exchangers 16 are the same as those in the first embodiment. Therefore, also in the heat exchanger 16 of the present embodiment, appropriate heat exchange can be performed between the three types of fluids of the refrigerant, the cooling water, and the outside air during the operation of the heat pump cycle 10 as in the first embodiment. In addition, the productivity of the heat exchanger capable of performing heat exchange between the three types of fluids can be improved without causing an increase in size.

  Furthermore, similarly to the second embodiment, the refrigerant tube 61 and the cooling medium tube 71 can be manufactured at low cost, so that the productivity can be further improved.

(Fourth embodiment)
In the present embodiment, an example in which the configuration of the heat pump cycle 10 is changed with respect to the first embodiment as illustrated in the overall configuration diagram of FIG. 16 will be described. FIG. 16 is an overall configuration diagram showing the refrigerant flow path and the like during the waste heat recovery operation in the present embodiment, the refrigerant flow in the heat pump cycle 10 is shown by a solid line, and the cooling water flow in the cooling water circulation circuit 40 is shown. This is indicated by a broken arrow.

Specifically, in the present embodiment, the indoor condenser 12 of the first embodiment is abolished, and the composite heat exchanger 16 of the first embodiment is disposed in the casing 31 of the indoor air conditioning unit 30. Yes. And among this heat exchanger 16, the outdoor heat exchange part 60 of 1st Embodiment is functioned as the indoor condenser 12. FIG. Hereinafter, the part functioning as the indoor condenser 12 in the heat exchanger 16 will be referred to as an indoor condensing part. On the other hand, for the outdoor heat exchanging part 60, the refrigerant circulating inside and the outside air blown from the blower fan 17 are heated. It is configured as a single heat exchanger to be exchanged. Other configurations are the same as those of the first embodiment. In the present embodiment, the defrosting operation is not executed, but the other operations are the same as those in the first embodiment.

  Therefore, during the waste heat recovery operation of the present embodiment, the air blown into the passenger compartment is heated by exchanging heat with the refrigerant discharged from the compressor 11 in the indoor evaporation section of the heat exchanger 16, and further heated in the indoor condensing section. The air blown into the passenger compartment can be heated by exchanging heat with cooling water in the radiator section 70 of the heat exchanger 16.

  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, the heat exchanger 16 described in the second and third embodiments may be applied to the heat pump cycle 10 of the present embodiment.

(Fifth embodiment)
This embodiment demonstrates the example which changed the structure of the heat exchanger 16 with respect to 1st Embodiment. A detailed configuration of the heat exchanger 16 of the present embodiment will be described with reference to FIGS. 17 and 18.

  FIG. 18 is an external perspective view of the heat exchanger 16 of the present embodiment, and FIG. 18 is a schematic perspective view for explaining the refrigerant flow and the cooling water flow of the heat exchanger 16, and each is a first perspective view. It is drawing corresponding to FIG. 5, FIG. 10 of embodiment. In FIG. 17, illustration of the tubes 61 and 71 of the heat exchanger 16, the outer fin 50, and the like is omitted for convenience of explanation.

  The outdoor heat exchanging unit 60 of the heat exchanger 16 of the present embodiment is configured with two rows of tank units 621 and 622 in which the refrigerant side header tank unit 62 is arranged along the flow direction X of the outside air. Of the two rows of tank portions 621 and 622, the first refrigerant tank portion 621 arranged on the upstream side in the flow direction X of the outside air partitions the internal space into two spaces 621a and 621b at the center in the longitudinal direction. A partition member 621c is disposed.

  The first refrigerant tank portion 621 is connected to a tube arranged on the windward side in the flow direction X of the outside air among the plurality of refrigerant tube upstream portions 611 and the refrigerant tube downstream portion 612, and circulates through the tubes. It functions as a collective distribution tank that collects or distributes refrigerant.

  A refrigerant introduction pipe 64 b for introducing a refrigerant is connected to one end side in the longitudinal direction of the first refrigerant tank section 621, and a refrigerant outlet pipe for leading out the refrigerant to the other longitudinal end side of the refrigerant side tank member 64. 64c is connected. The refrigerant introduction pipe 64b communicates with the distribution space 621a among the two spaces 621a and 621b formed inside the first refrigerant tank section 621, and the refrigerant outlet pipe 64c is formed inside the first refrigerant tank section 621. Of the two spaces 621a and 621b formed in, the space communicates with the collective space 621b.

  In addition, of the two rows of tank portions 621 and 622 that constitute the refrigerant side header tank portion 62, the second refrigerant tank portion 622 disposed on the downstream side in the flow direction X of the outside air includes a plurality of refrigerant tube upstream portions 611. The refrigerant tube downstream portion 612 is connected to a tube arranged on the leeward side in the flow direction X of the outside air, and functions as a collective distribution tank that collects or distributes the refrigerant flowing through the tube. And the both ends of the longitudinal direction of the 2nd refrigerant | coolant tank part 622 are obstruct | occluded by the obstruction | occlusion member.

  Here, among the plurality of refrigerant tubes 61, a tube group through which the refrigerant introduced into the outdoor heat exchange unit 60 through the refrigerant introduction pipe 64b constitutes the upstream refrigerant tube group 60a, Among the refrigerant tubes 61, a tube group that flows out from the upstream refrigerant tube group 60a and through which the refrigerant derived from the refrigerant outlet pipe 64c flows constitutes the downstream refrigerant tube group 60b.

  In the refrigerant tube 61 constituting the upstream refrigerant tube group 60 a, the refrigerant tube upstream portion 611 is arranged on the upstream side in the outside air flow direction X with respect to the refrigerant tube downstream portion 612. In the refrigerant tube 61 constituting the downstream refrigerant tube group 60 b, the refrigerant tube upstream portion 611 is disposed on the downstream side in the outside air flow direction X with respect to the refrigerant tube downstream portion 612.

  Therefore, the outdoor heat exchanging unit 60 of the present embodiment has the first refrigerant tank unit 621 of the refrigerant side header tank unit 62 via the refrigerant introduction pipe 64b as shown by the solid line arrow in the schematic perspective view of FIG. Refrigerant introduced into the distribution space 621a is in the upstream air flow direction X in the upstream refrigerant tube group 60a, the refrigerant tube upstream portion 611 on the upstream side in the outdoor air flow direction X → the refrigerant side turn portion 61e, and in the outdoor air flow direction X in the upstream refrigerant tube group 60a. It flows while making a U-turn in the order of the refrigerant tube downstream portion 612. Thereafter, the refrigerant that has flowed from the refrigerant tube downstream portion 612 into the second refrigerant tank portion 622 flows into the downstream refrigerant tube group 60b in the outside air flow direction X in the leeward refrigerant tube upstream portion 611 → refrigerant side turn portion 61e → downstream refrigerant tube. The outside air flow direction X in the group 60b flows while making a U-turn in the order of the refrigerant tube downstream portion 612 on the leeward side.

  Returning to FIG. 17, the radiator section 70 of the heat exchanger 16 according to the present embodiment includes the two tank sections 721 and 722 in which the cooling medium side header tank section 72 is arranged along the flow direction X of the outside air. . Of the two rows of tank portions 721 and 722, the first cooling medium tank portion 721 disposed on the upstream side in the outside air flow direction X is a partition member that divides the internal space into two spaces at the center in the longitudinal direction. 721c is arranged.

  The first cooling medium tank portion 721 is connected to a tube disposed on the windward side in the flow direction X of the outside air among the plurality of cooling medium tube upstream portions 711 and the cooling medium tube downstream portions 712, and the tubes It functions as a collection / distribution tank that collects or distributes the refrigerant flowing through

  A cooling medium introduction pipe 74 b for introducing cooling water is connected to one end side in the longitudinal direction of the first cooling medium tank portion 721, and cooling water is supplied to the other end side in the longitudinal direction of the cooling medium side tank member 74. A cooling medium outlet piping 74c to be led out is connected. The cooling medium introduction pipe 74b communicates with the distribution space 721a among the two spaces 721a and 721b formed inside the first cooling medium tank section 721, and the cooling medium outlet pipe 74c is the first cooling medium tank. Of the two spaces 721a and 721b formed inside the portion 721, the space 721b communicates.

  In addition, of the two rows of tank portions 721 and 722 constituting the cooling medium side header tank portion 72, the second cooling medium tank portion 722 arranged on the downstream side in the outside air flow direction X includes a plurality of cooling medium tubes. Of the upstream portion 711 and the cooling medium tube downstream portion 712, it is connected to a tube disposed on the leeward side in the flow direction X of the outside air, and functions as a collection / distribution tank that collects or distributes the refrigerant flowing through the tube. To do. Then, both end sides in the longitudinal direction of the second cooling medium tank portion 722 are closed by a closing member.

  Here, among the plurality of cooling medium tubes 71, the tube group through which the cooling water introduced into the radiator section 70 through the cooling medium introduction pipe 74b constitutes the upstream side cooling medium tube group 70a. Among the cooling medium tubes 71, the tube group that flows out from the upstream side cooling medium tube group 70a and through which the cooling water led out from the cooling medium outlet pipe 74c flows constitutes the downstream side cooling medium tube group 70b. .

  In the cooling medium tube 71 constituting the upstream cooling medium tube group 70 a, the cooling medium tube upstream portion 711 is disposed on the upstream side in the outside air flow direction X with respect to the cooling medium tube downstream portion 712. Further, in the cooling medium tube 71 constituting the downstream side cooling medium tube group 70 b, the cooling medium tube upstream portion 711 is disposed on the downstream side in the outside air flow direction X with respect to the cooling medium tube downstream portion 712.

  Accordingly, the radiator section 70 of the present embodiment is configured so that the first cooling medium tank section 721 of the cooling medium side header tank section 72 is interposed via the refrigerant introduction pipe 64b as shown by a dotted arrow in the schematic perspective view of FIG. The refrigerant introduced into the distribution space 721a flows in the outside air flow direction X in the upstream side cooling medium tube group 70a. The cooling medium tube upstream part 711 on the windward side → the cooling medium side turn part 71e → the outside air flow direction in the upstream side cooling medium tube group 70a. It flows while making a U-turn in the order of the cooling medium tube downstream portion 712 on the leeward side of X. Thereafter, the refrigerant that has flowed from the cooling medium tube downstream portion 712 into the second cooling medium tank portion 722 flows into the downstream cooling medium tube group 70b in the outside air flow direction X, the cooling medium tube upstream portion 711 on the leeward side, and the cooling medium side turn portion 71e. → The downstream side cooling medium tube group 70b flows while making a U-turn in the order of the cooling medium tube downstream portion 712 on the windward side in the outside air flow direction X.

  Here, in the heat exchanger 16 of the present embodiment, the refrigerant tube upstream portion 611 of the upstream refrigerant tube group 60a and the cooling medium tube upstream portion 711 of the upstream cooling medium tube group 70a are stacked in the tubes 61 and 71, respectively. The refrigerant tube downstream portion 612 of the upstream refrigerant tube group 60a and the cooling medium tube downstream portion 712 of the upstream cooling medium tube group 70a are arranged side by side in the stacking direction of the tubes 61 and 71. Has been placed.

  In the heat exchanger 16 of this embodiment, the refrigerant tube upstream portion 611 of the downstream refrigerant tube group 60b and the cooling medium tube upstream portion 711 of the downstream cooling medium tube group 70b are stacked in the stacking direction of the tubes 61 and 71. The refrigerant tube downstream portion 612 of the downstream refrigerant tube group 60b and the cooling medium tube downstream portion 712 of the downstream cooling medium tube group 70b are arranged side by side in the stacking direction of the tubes 61 and 71. Has been.

  In the outdoor heat exchanger 60, the refrigerant flows in the upstream refrigerant tube group 60a from the upstream side in the flow direction of the outside air to the downstream side, and in the downstream refrigerant tube group 60b, the refrigerant flows from the downstream side in the flow direction of the outside air to the upstream side. . Similarly, in the radiator section 70, the cooling water flows in the upstream side cooling medium tube group 70a from the upstream side in the flow direction of the outside air to the downstream side, and the cooling water flows in the downstream side cooling medium tube group 70b from the downstream side in the flow direction of the outside air. Flows to the side.

  Accordingly, the refrigerant tubes 61 and the cooling medium tubes 71 constituting the upstream refrigerant tube group 60a and the upstream cooling medium tube group 70a are in the same direction from the leeward side in the flow direction X of the outside air to the leeward side. It is configured to flow. Further, the refrigerant tube 61 and the cooling medium tube 71 constituting the downstream refrigerant tube group 60b and the downstream cooling medium tube group 70b are arranged so that the refrigerant and the cooling water flow from the leeward side to the windward side in the flow direction X of the outside air. It is configured to flow in the same direction.

  The configuration and operation of the heat pump cycle 10 including other heat exchangers 16 are the same as those in the first embodiment. Therefore, also in the heat exchanger 16 of the present embodiment, appropriate heat exchange can be performed between the three types of fluids of the refrigerant, the cooling water, and the outside air during the operation of the heat pump cycle 10 as in the first embodiment. In addition, the productivity of the heat exchanger capable of performing heat exchange between the three types of fluids can be improved without causing an increase in size.

  In addition to this, in the heat exchanger 16 of the present embodiment, the refrigerant tube upstream portion 611 of each refrigerant tube 61 constituting the upstream refrigerant tube group 60a is arranged in the outside air flow direction X with respect to the refrigerant tube downstream portion 612. The cooling medium tube upstream portion 711 of each cooling medium tube 71 constituting the upstream side cooling medium tube group 70a is disposed on the upstream side in the outside air flow direction X with respect to the cooling medium tube downstream portion 712. It is configured to do.

  According to this, in the operation state in which the refrigerant introduced into the outdoor heat exchange unit 60 and the cooling medium introduced into the radiator unit 70 both have a temperature higher than the outside air, the refrigerant flow upstream of the upstream refrigerant tube group 60a, On the upstream side of the cooling water flow in the upstream side cooling medium tube group 70a, the temperature difference between the refrigerant and the outside air and the temperature difference between the cooling medium and the outside air are secured and released while reducing the temperature difference between the refrigerant and the cooling water. The amount of heat can be increased. As a result, the difference in the amount of thermal strain between the refrigerant tube 61 and the cooling medium tube 71 can be reduced.

  Further, in the heat exchanger 16 of the present embodiment, the refrigerant tube upstream portion 611 of each refrigerant tube 61 constituting the downstream side refrigerant tube group 60b is arranged downstream of the refrigerant tube downstream portion 612 in the outside air flow direction X. In addition, the cooling medium tube upstream portion 711 of each cooling medium tube 71 of the downstream side cooling medium tube group 70b is disposed downstream of the cooling medium tube downstream portion 712 in the outside air flow direction X.

  According to this, in the operation state in which the refrigerant introduced into the outdoor heat exchange unit 60 and the cooling medium introduced into the radiator unit 70 both have a temperature higher than the outside air, the refrigerant flow downstream of the downstream refrigerant tube group 60b and On the downstream side of the cooling water flow in the downstream side cooling medium tube group 70b, the heat quantity of the refrigerant and the cooling water can be sufficiently dissipated to the outside air. As a result, the performance of the heat exchanger 16 can be improved.

  As is clear from the above description, the upstream refrigerant tube group 60a of the present embodiment corresponds to the upstream first tube group described in the claims, and the downstream refrigerant tube 60b of the present embodiment. Corresponds to the downstream first tube group. The upstream side cooling medium tube group 70a of the present embodiment corresponds to the upstream side second tube group described in the claims, and the downstream side cooling medium tube 70b of the present embodiment is the downstream side second tube. Corresponds to the group.

(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, as a configuration of the heat exchanger 16, a tank-and-tube type having two heat exchanging portions 60, 70 having tubes (61, 71) and collective distribution tanks (62, 72). Although the example comprised to the heat exchanger structure was demonstrated, the structure of each heat exchange part 60 and 70 is not limited to this.

  For example, a plurality of plate members in which a tube and a tank portion communicating with the tube are formed by joining a pair of plate-like members together in the middle are stacked and disposed with the outer fin 50 interposed therebetween. A so-called drone cup type heat exchanger structure may be employed.

  In this type of drone cup type heat exchanger structure, a plurality of plate members are stacked and the tank portions of the plate members communicate with each other, whereby the refrigerant-side header tank portion 62 and the cooling medium in the above-described embodiment are used. A configuration corresponding to the side header tank portion 72 can be formed.

  (2) In the above embodiment, the refrigerant side header tank in which the internal space is partitioned into the collecting spaces 62a and 72a and the distribution spaces 62b and 72b by joining the plate members 63 and 73 and the tank members 64 and 74 together. Although the example which comprised the part 62 and the cooling medium side header tank part 72 was demonstrated, the structure of each header tank part 62 and 72 is not limited to this.

  For example, the header tank portion may be constituted by two tubular members, and the internal space of each tubular member may be a collective space or a distribution space. Thereby, the pressure | voltage resistance of each header tank part can be improved.

  (3) In the above-described embodiment, the example in which the refrigerant tubes 61 and the cooling medium tubes 71 are alternately stacked has been described. However, the arrangement of the refrigerant tubes 61 and the cooling medium tubes 71 is not limited thereto.

  For example, in the heat exchanger 16 of the first and third embodiments, as shown in FIG. 19A, a plurality of (N) refrigerant tubes 61 are continuously stacked and arranged. The cooling medium tubes 71 may be continuously stacked. At this time, the number of the refrigerant tubes 61 and the cooling medium tubes 71 that are continuously stacked may be the same or different.

  For example, in the heat exchanger 16 of the second embodiment, as shown in FIGS. 19B to 19D, the refrigerant tube 61 is disposed on the upstream side with respect to the flow direction X of the outside air, and the downstream side. The cooling medium tube 71 may be arranged on the side.

  FIG. 19 schematically shows a longitudinal sectional view of the header tank portion of the heat exchanger 16. In FIG. 19, the refrigerant tube 61 is indicated by hatching and the cooling medium tube 71 is indicated by dot hatching for clarity of illustration.

  Here, as shown in FIG. 19, when the arrangement form in which the refrigerant tubes 61 are adjacent to each other or the arrangement form in which the cooling medium tubes 71 are adjacent to each other is adopted, the refrigerant tubes 61 are formed between the adjacent refrigerant tubes 61. It is desirable to arrange the outer fins 50 in the space and also in the space formed between the adjacent cooling medium tubes 71.

  According to this, the outer fin 50 will be arrange | positioned in all the spaces formed between each tube 61 and 71 and the tube 61 for refrigerant | coolants or the tube 71 for cooling media adjacent to this, and the outer fin 50 This facilitates heat exchange between the fluid (refrigerant and cooling water) flowing through the tubes 61 and 71 and the outside air, so that the difference in thermal strain between the refrigerant tube 61 and the cooling medium tube 71 is reduced (reduced). Can do. As a result, damage to the heat exchanger 16 can be suppressed.

  (4) In the first embodiment described above, of the refrigerant tube 61 and the cooling medium tube 71, the cooling medium tube upstream portion 711 of the cooling medium tube 71 is in the flow direction of the outside air with respect to the cooling medium tube downstream portion 712. Although the example arrange | positioned in the upstream of X was demonstrated, it is not limited to this.

  For example, among the refrigerant tube 61 and the cooling medium tube 71, the refrigerant tube upstream portion 611 of the refrigerant tube 61 may be disposed upstream of the refrigerant tube downstream portion 612 in the flow direction X of the outside air. .

  According to this, for example, in the operation state in which the temperature of the refrigerant introduced into the outdoor heat exchange unit 60 is higher than the temperature of the cooling medium and the outside air, the refrigerant and the outside air are in the refrigerant flow upstream of the refrigerant tube 61. A temperature difference can be secured and the amount of heat radiation can be increased. Thereby, the temperature difference between the refrigerant and the cooling water can be reduced, and the difference in thermal strain between the refrigerant tube 61 and the cooling medium tube 71 can be alleviated. In this example, the refrigerant corresponds to the “high temperature side fluid”, the refrigerant tube 61 constitutes the “high temperature side tube”, and the refrigerant tube upstream portion 611 of the refrigerant tube 61 is the “high temperature side tube upstream portion”. Further, the refrigerant tube downstream portion 612 of the refrigerant tube 61 constitutes a “high temperature side tube downstream portion”. Further, the cooling water corresponds to the “low temperature side fluid”, the cooling medium tube 71 constitutes the “low temperature side tube”, and the cooling medium tube upstream portion 711 of the cooling medium tube 71 is the “low temperature side tube upstream portion”. Furthermore, the cooling medium tube downstream portion 712 of the cooling medium tube 71 constitutes a “low temperature side tube downstream portion”.

  (5) In the first embodiment described above, the refrigerant tube upstream portion 611 of the refrigerant tube 61 and the cooling medium tube downstream portion 712 of the cooling medium tube 71 are arranged in the stacking direction of the tubes 61, 71. The example in which the refrigerant tube downstream portion 612 and the cooling medium tube upstream portion 711 are arranged so as to be aligned in the stacking direction of the tubes 61 and 71 has been described, but is not limited thereto.

  For example, the refrigerant tube upstream portion 611 of the refrigerant tube 61 and the cooling medium tube upstream portion 711 of the cooling medium tube 71 are arranged so as to be aligned in the stacking direction of the tubes 61, 71. It is good also as a structure arrange | positioned so that the medium tube downstream part 712 may be located in a line with the lamination direction of each tube 61,71.

  In such a configuration, the refrigerant flowing through the refrigerant tube 61 and the cooling water flowing through the cooling medium tube 71 are opposed to each other in the longitudinal direction of the tubes 61, 71, while the flow of outside air. In the direction, the flow directions are the same as each other (windward → leeward or leeward → windward) (partly parallel flow structure).

  According to the heat exchanger 16 having such a structure, as compared with the heat exchanger 16 shown in the first embodiment, the refrigerant and the cooling medium tube that circulate through the refrigerant tube 61 as a whole because the heat exchange performance is lowered. The temperature difference with the cooling medium flowing through 71 can be reduced.

  Here, in the heat exchanger 16 having a partially parallel flow structure, the reason why the temperature difference between the refrigerant flowing through the refrigerant tube 61 and the cooling medium flowing through the cooling medium tube 71 can be reduced will be described with reference to FIG. explain. FIG. 20 is an explanatory diagram for explaining the influence on the temperature difference between the refrigerant and the cooling water in each tube due to the difference in the structure of the heat exchanger. The solid line in FIG. 20 shows a schematic temperature change (the black circle is the inflow part and the black diamond is the outflow part) of the fluid (high temperature side fluid) having the higher temperature of the refrigerant and the cooling water. The schematic temperature change of the fluid (low temperature side fluid) with the lower temperature in the heat exchanger 16 having the parallel flow structure is shown, and the two-dot chain line indicates the counter flow structure (the heat exchanger 16 described in the first embodiment). ) Shows a schematic temperature change of the fluid on the low temperature side. Note that the alternate long and short dash line indicates the low-temperature side fluid flowing out of the tube when the heat exchanger 16 has a partially parallel flow structure in an operating state where the temperature of the outside air is lower than the temperature of the refrigerant and the cooling water. The temperature change when the outflow temperature Tl2 and the outflow temperature Tl2 ′ of the low-temperature side fluid flowing out from the tube when the heat exchanger 16 having the counterflow structure is made to coincide is shown.

  As described above, the heat exchanger 16 having a partially parallel flow structure has lower heat exchange performance than the heat exchanger 16 shown in the first embodiment. For this reason, as shown by the one-dot chain line and the two-dot chain line in FIG. 20, in the heat exchanger 16 having a partially parallel flow structure, the inflow temperature Tl1 of the low-temperature side fluid flowing into the tube is the heat shown in the first embodiment. The temperature is higher than the inflow temperature Tl1 ′ of the low temperature side fluid flowing into the exchanger 16.

  That is, the temperature difference ΔT between the inflow temperature Th1 of the high temperature side fluid flowing into the heat exchanger 16 and the inflow temperature Tl1 of the low temperature side fluid in the heat exchanger 16 having a partially parallel flow structure is the heat shown in the first embodiment. This is smaller than the temperature difference ΔT ′ between the inflow temperature Tl1 ′ of the high temperature side fluid flowing into the exchanger 16 and the inflow temperature Tl1 ′ of the low temperature side fluid.

  Therefore, in the heat exchanger 16 having a partially parallel flow structure, as compared with the heat exchanger 16 shown in the first embodiment, the refrigerant flowing through the refrigerant tube 61 and the cooling medium flowing through the cooling medium tube 71 as a whole. And the temperature difference can be reduced. As a result, the difference in the amount of thermal strain between the refrigerant tube 61 and the cooling medium tube 71 can be reduced. In this example, the case where the temperature of the outside air is in an operating state lower than the temperature of the refrigerant and the cooling water has been described. However, a partially parallel flow structure is used regardless of the relationship between the temperature of the outside air and the temperature of the refrigerant and the cooling water. Compared with the heat exchanger 16 shown in the first embodiment, the heat exchanger 16 includes a refrigerant flowing in the refrigerant tube 61 as a whole and the cooling medium tube 71 in the heat exchanger 16 having a partially parallel flow structure. It is possible to reduce the temperature difference from the circulating cooling medium.

  Further, in the heat exchanger 16 having a partially parallel flow structure, the refrigerant tube upstream portion 611 and the cooling medium tube upstream portion 711 are arranged upstream of the refrigerant tube downstream portion 612 and the cooling medium tube downstream portion 712 in the flow direction of the outside air. It is desirable that the configuration be arranged on the side.

  According to this, in the operation state where both the refrigerant introduced into the outdoor heat exchange unit 60 and the cooling medium introduced into the radiator unit 70 have a temperature higher than the outside air, the temperature difference between the refrigerant and the outside air, and the cooling water A heat difference can be increased by securing a temperature difference from the outside air. As a result, the difference in the amount of thermal strain between the refrigerant tube 61 and the cooling medium tube 71 can be alleviated, and damage to the heat exchanger 16 can be suppressed.

  (6) In the first embodiment described above, 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 air is blown by the blower fan 17 as the third fluid. Although the example which employ | adopted outside air was demonstrated, the 1st-3rd fluid is not limited to this. For example, as in the third embodiment, vehicle interior air may be employed as the third fluid.

  For example, the first fluid may be a high-pressure side refrigerant of the heat pump cycle 10 or a low-pressure side refrigerant.

  For example, the second fluid may employ cooling water that cools electric devices such as an inverter that supplies electric power to the engine and the traveling electric motor MG. Moreover, the oil for cooling may be employ | adopted as a 2nd fluid, a 2nd heat exchange part may be functioned as an oil cooler, and a heat storage agent, a cool storage agent, etc. may be employ | adopted as a 2nd fluid.

  The first to third fluids are not limited to fluids having different physical properties and components. As the first to third fluids, fluids having the same physical properties and components, or fluids having different fluid states such as temperature, gas phase, and liquid phase may be employed. For example, the high-pressure side refrigerant of the heat pump cycle 10 may be adopted as the first fluid, and the low-pressure side refrigerant of the heat pump cycle 10 may be adopted as the second fluid. Further, for example, when a circuit in which cooling water for cooling the engine circulates and a circuit in which cooling water for cooling the inverter circulates are different, the engine cooling water is employed as the first fluid, and the second You may employ | adopt the cooling water of an inverter as a fluid.

  As for the temperature relationship of the first to third fluids, the temperature of the third fluid is lower than the temperature of the higher fluid (high temperature side fluid) of the first fluid and the second fluid, and Of the first fluid and the second fluid, it is desirable that the temperature of the fluid having the lower temperature (the low temperature side fluid) is higher. In such a temperature relationship, the temperature of the high temperature side fluid decreases in the heat exchanger 16 and the temperature of the low temperature side fluid increases, so the temperature difference between the first fluid and the second fluid can be reduced. . As a result, the difference in the amount of thermal strain between the tubes 61 and 71 can be alleviated, and damage to the heat exchanger 16 can be effectively suppressed.

  In addition, when the heat pump cycle 10 to which the heat exchanger 16 of the present invention is applied is applied to a stationary air conditioner, a cold storage, a vending machine cooling heating device, etc., the heat pump cycle 10 is compressed as the second fluid. You may employ | adopt the cooling water which cools an engine, an electric motor, other electric equipment, etc. as a drive reduction of a machine.

  Furthermore, although the above-mentioned embodiment demonstrated the example which applied the heat exchanger 16 of this invention to the heat pump cycle (refrigeration cycle), application of the heat exchanger 16 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.

  (7) In the embodiment described above, an example in which the refrigerant tube 61 of the outdoor heat exchange unit 60, the cooling medium tube 71 of the radiator unit 70, and the outer fin 50 are formed of aluminum alloy (metal) and brazed and joined is described. However, as a matter of course, the outer fin 50 may be formed of another material having excellent heat conductivity (for example, carbon nanotubes) and bonded by bonding means such as adhesion.

  Here, FIG. 21 is a schematic partial perspective view of a heat exchanger 16 according to another embodiment, and FIG. 22 is an explanatory diagram for explaining an outer fin 50 according to another embodiment. 22A is a partial front view of the outer fin 50, FIG. 22B is a DD cross-sectional view shown in FIG. 22A, and FIG. 22C is FIG. It is an enlarged view of the E section of a).

  In the configuration in which the outer fin 50 is joined to the tubes 61 and 71 as in the above-described embodiments, as shown in FIGS. 21 and 22, a plurality of slits 50 a for locally reducing the rigidity of the outer fin 50. It is desirable to form. The slit 50 a can be configured by a through-hole penetrating the front and back of the outer fin 50 or a notch formed in the outer periphery of the outer fin 50.

  According to this, when a difference in thermal strain occurs between the tubes 61 and 71, it is possible to absorb the stress acting on the tubes 61 and 71 by the slits 50a of the outer fin 50. Further, in the configuration in which the plurality of slits 50a are provided in the outer fin 50, it is possible to suppress damage to the heat exchanger 16 when a difference in the amount of thermal strain between the tubes 61 and 71 occurs.

  (8) In the first embodiment described above, the refrigerant tubes 61 and the cooling medium are used with the plate-like members 61a, 61b, 71a, 71b fitted into the inner fins 65, 75 during the tube / tank temporary fixing process. Although it has been described that the tube 71 is temporarily fixed, positioning portions of the inner fins 65 and 75 may be formed on the plate-like members 61a, 61b, 71a, and 71b.

  Such a positioning portion may be formed, for example, by providing a protruding portion projecting inwardly in the refrigerant flow path 61c, the cooling medium flow path 71c, the turn portions 61e and 71e, and the enlarged portions 61f and 71f.

  (9) In the second and third embodiments described above, the inner fins 65 and 75 disposed in the refrigerant tube 61 and the cooling medium tube 71 are not mentioned, but the inner fins 65 and 75 are employed. In this case, it is desirable that the flat tube is bent and then inserted into the upstream and downstream fluid passages of the turn portions 61e and 71e. Thereby, when bending a flat tube, it can suppress that an inner fin deform | transforms.

  (10) 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. Therefore, the cooling water temperature sensor 52 can be abolished by adopting a thermostat valve.

  (11) In the above-described embodiment, an example in which a normal chlorofluorocarbon refrigerant is employed as the refrigerant has been described, but the type of the refrigerant is not limited thereto. Natural refrigerants such as carbon dioxide, hydrocarbon refrigerants, and the like may be employed. Furthermore, the heat pump cycle 10 may constitute a supercritical refrigeration cycle in which the refrigerant discharged from the compressor 11 is equal to or higher than the critical pressure of the refrigerant.

16 heat exchanger 16a outdoor air passage 50 outer fin 60 outdoor heat exchange part 61 refrigerant tube 61a, 61b plate member 61e refrigerant side turn part 62 refrigerant side header tank part 65 inner fin 70 radiator part 71 cooling medium tubes 71a, 71b Plate-like member 71e Cooling medium side turn part 72 Cooling medium side header tank part 75 Inner fin

Claims (15)

A plurality of first tubes (61) through which the first fluid circulates and an assembly or distribution of the first fluids that extend in the stacking direction of the plurality of first tubes (61) and circulate through the first tubes (61). A first heat exchanging unit (60) for exchanging heat between the first fluid and the third fluid flowing around the first tube (61).
A plurality of second tubes (71) through which the second fluid flows, and a set or distribution of the second fluids extending in the stacking direction of the plurality of second tubes (71) and flowing through the second tubes (71). A second tank part (72) for performing heat exchange, and a second heat exchange part (70) for exchanging heat between the second fluid and the third fluid flowing around the second tube (71),
The first tube (61) and the second tube (71) are disposed between the first tank part (62) and the second tank part (72),
At least one of the plurality of first tubes (61) is disposed between the plurality of second tubes (71),
At least one of the plurality of second tubes (71) is disposed between the plurality of first tubes (61),
The space formed between the first tube (61) and the second tube (71) forms a third fluid passage (16a) through which the third fluid flows,
The third fluid passage (16a) promotes heat exchange in both heat exchange sections (60, 70), and the first fluid and the second tube (circulating through the first tube (61)). 71) outer fins (50) that allow heat transfer with the second fluid flowing through the
The first tube (61) is provided with a first turn part (61e) for changing the flow direction of the first fluid,
The second tube (71) is provided with a second turn part (71e) for changing the flow direction of the second fluid,
The first turn part (61e) is positioned closer to the second tank part (72) than the first tank part (62),
The heat exchanger according to claim 1, wherein the second turn part (71e) is positioned closer to the first tank part (62) than the second tank part (72). The temperature of the first fluid introduced into the first heat exchange part (60) is different from the temperature of the second fluid introduced into the second heat exchange part (70),
The outer fin (50) is formed in a space formed between the first and second tubes (61, 71) and the first and second tubes (61, 71) arranged adjacent to the first and second tubes (61, 71). The heat exchanger according to claim 1, wherein the heat exchanger is arranged.   The first tube (61) and the second tube (71) are both fixed to both the first tank part (62) and the second tank part (72). The heat exchanger according to 1 or 2. Of the first fluid introduced into the first heat exchange unit (60) and the second fluid introduced into the second heat exchange unit (70), a fluid having a higher temperature is defined as a high temperature side fluid,
Of the first tube (61) and the second tube (71), the high temperature side tube is located upstream of the first and second turn portions (61e, 71e) of the high temperature side tube through which the high temperature side fluid flows. As upstream,
Of the first tube (61) and the second tube (71), the high temperature side tube is located downstream of the first and second turn portions (61e, 71e) of the high temperature side tube through which the high temperature side fluid flows. When the downstream part
The temperature of the third fluid is lower than the temperature of the high temperature side fluid,
Among the plurality of high temperature side tubes, at least a part of the high temperature side tube upstream portion is disposed on the upstream side in the flow direction of the third fluid with respect to the high temperature side tube downstream portion. The heat exchanger according to any one of claims 1 to 3. Of the first fluid introduced into the first heat exchange unit (60) and the second fluid introduced into the second heat exchange unit (70), a fluid having a lower temperature is a low temperature side fluid,
Of the first tube (61) and the second tube (71), the low temperature side tube is located upstream of the first and second turn portions (61e, 71e) of the low temperature side tube through which the low temperature side fluid flows. As upstream,
Of the first tube (61) and the second tube (71), the low temperature side tube is located downstream of the first and second turn portions (61e, 71e) of the low temperature side tube through which the low temperature side fluid flows. When the downstream part
The temperature of the third fluid is lower than the temperature of the low temperature side fluid,
Among the plurality of low temperature side tubes, at least a part of the low temperature side tube upstream portion is arranged on the upstream side in the flow direction of the third fluid with respect to the low temperature side tube downstream portion. The heat exchanger according to claim 4.   The temperature of the third fluid is the higher of the first fluid introduced into the first heat exchange part (60) and the second fluid introduced into the second heat exchange part (70). The heat exchanger according to any one of claims 1 to 4, wherein the temperature is lower than the temperature of the fluid and higher than the temperature of the lower fluid. An upstream side of the first turn part (61e) of the first tube (61) is a first tube upstream part (611),
The first tube downstream portion (612) is the downstream side of the first turn portion (61e) of the first tube (61),
Furthermore, an upstream side of the second turn portion (71e) of the second tube (71) is a second tube upstream portion (711),
When the second tube downstream portion (712) is the downstream side of the second turn portion (71e) of the second tube (71),
The first tube upstream portion (611) and the second tube upstream portion (711) are arranged so as to be aligned in the stacking direction of the first and second tubes (61, 71),
The said 1st tube downstream part (612) and the said 2nd tube downstream part (712) are arrange | positioned so that it may be located in a line with the lamination direction of the said 1st, 2nd tube (61, 71). Item 4. The heat exchanger according to any one of Items 1 to 3.   The first tube upstream portion (611) and the second tube upstream portion (711) flow of the third fluid with respect to the first tube downstream portion (612) and the second tube downstream portion (712). The heat exchanger according to claim 7, wherein the heat exchanger is disposed upstream in the direction. The plurality of first tubes (61) include an upstream first tube group (60a) through which the first fluid introduced into the first heat exchange section (60) flows, and the upstream first tube group ( 60a) having a downstream first tube group (60b) through which the first fluid flowing out from the first heat exchange section (60) flows,
The plurality of second tubes (71) include an upstream second tube group (70a) through which the second fluid introduced into the second heat exchange unit (70) flows, and the upstream second tube group ( 70a) having a downstream second tube group (70b) through which the second fluid flowing out from the second heat exchange section (70) flows,
The first tube upstream portion (611) and the second tube upstream portion (711) in the upstream first tube group (60a) and the upstream second tube group (70a) are the first tube downstream portion ( 612) and the second tube downstream portion (712), the heat exchanger according to claim 7, wherein the heat exchanger is disposed upstream in the flow direction of the third fluid.   The first tube upstream portion (611) and the second tube upstream portion (711) in the downstream first tube group (60b) and the downstream second tube group (70b) are the first tube downstream portion ( 612) and the second tube downstream portion (712), the heat exchanger according to claim 9, wherein the heat exchanger is disposed on the downstream side in the flow direction of the third fluid.   The outer fin (50) is joined to the first and second tubes (61, 71) and has a plurality of slits (50a) for locally weakening rigidity. The heat exchanger according to any one of claims 1 to 10.   The refrigerant passage area of at least one intermediate part of the first turn part (61e) and the second turn part (71e) is formed larger than the fluid passage area of the fluid inflow part and the fluid outflow part. The heat exchanger according to claim 1, wherein the heat exchanger is a heat exchanger. At least one of the first tube (61) and the second tube (71) has an inner fin (65) that promotes heat exchange between the first fluid or the second fluid and the third fluid flowing therethrough. , 75) are arranged,
The end of the inner fin (65, 75) protrudes into the internal space of the first turn part (61e) or the second turn part (71e). The heat exchanger according to one.   The first tube (61) and the second tube (71) are configured by a plate tube formed by bonding a pair of plate-like members (61a, 61b, 71a, 71b). The heat exchanger according to any one of claims 1 to 13.   The said 1st tube (61) and the said 2nd tube (71) are formed by bending the flat tube in which the longitudinal cross section was formed in flat shape, The 1st thru | or 13 characterized by the above-mentioned. The heat exchanger as described in any one of these.

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