JP2016161186A - Complex type heat exchanger - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a complex type heat exchanger for improving a heating efficiency at a freezing cycle.SOLUTION: A complex type heat exchanger 52 comprises: a first tank part 52a connected to one end of a heat radiating part 52b for radiating heat of a cooling medium to surrounding atmosphere where the cooling medium flows; a second tank part 52c connected to the other end of the heat radiating part 52b where the cooling medium flows; and a heat exchanging part 22 provided in the second tank part 52c where refrigerant of freezing cycle 2 flows and the cooling medium and the refrigerant perform heat exchanging operation. The first tank part 52b is provided with only any one of a first flow-in part 61c capable of flowing-in the cooling medium and a first discharging part 62c capable of discharging the cooling medium, the second tank part 52c is provided with second flow-in parts 61a and 62a capable of flowing-in the cooling medium and second discharging parts 61b and 62b capable of discharging the cooling medium.SELECTED DRAWING: Figure 3

Description

  The present invention relates to a composite heat exchanger.

  Patent Document 1 discloses a composite heat exchanger in which a water-cooled condenser is provided in an inflow side tank of a sub-radiator, and heat exchange is performed between cooling water that has cooled high-powered equipment and a refrigerant for air conditioning.

JP 2014-173748 A

  According to the above technique, the air-conditioning refrigerant before flowing into the air-cooled condenser can be cooled by the water-cooled condenser, and the cooling efficiency can be improved.

  However, in the above technique, only the improvement of the cooling efficiency is considered, and there is room for examination on the heating efficiency.

  This invention is invented in view of such a point, and it aims at improving heating efficiency in a composite-type heat exchanger.

  A composite heat exchanger according to an aspect of the present invention includes a heat dissipating unit that dissipates heat of the cooling medium to the outside air, a first tank unit that is connected to one end of the heat dissipating unit, and through which the cooling medium flows, and the other end of the heat dissipating unit. And a second tank part through which the cooling medium flows, and a heat exchange part that is provided in the second tank part, flows through the refrigerant of the refrigeration cycle, and exchanges heat between the cooling medium and the refrigerant. Is provided with only one of a first inflow portion capable of flowing in the cooling medium and a first discharge portion capable of discharging the cooling medium, and the second inflow portion capable of inflowing the cooling medium in the second tank portion. And a second discharge part capable of discharging the cooling medium.

  According to this aspect, it is possible to switch the inflow direction of the cooling medium flowing into the composite heat exchanger during cooling and heating, and improve the heating efficiency of the refrigeration cycle.

It is a block diagram of the vehicle air conditioner of 1st Embodiment. It is a block diagram of the power module cycle of 1st Embodiment. It is the schematic of the radiator of 1st Embodiment. It is a figure explaining the flow of the refrigerant | coolant at the time of air_conditionaing | cooling of 1st Embodiment, and cooling water. It is a figure explaining the flow of the refrigerant at the time of heating of a 1st embodiment, and cooling water. In the power module cycle of 1st Embodiment, it is a figure explaining the flow of the cooling water at the time of cooling. It is a figure explaining the flow of the cooling water at the time of heating in the power module cycle of 1st Embodiment. It is a block diagram of the power module cycle of 2nd Embodiment. It is the schematic of the radiator of 2nd Embodiment. It is a figure explaining the flow of the cooling water at the time of air_conditioning | cooling of 2nd Embodiment. It is a figure explaining the flow of the cooling water at the time of the heating of 2nd Embodiment.

  Hereinafter, embodiments of the present invention will be described with reference to the accompanying drawings.

  A first embodiment of the present invention will be described with reference to FIG. FIG. 1 is a block diagram of an air conditioner 1 for a vehicle.

  The vehicle air conditioner 1 includes a refrigeration cycle 2 in which refrigerant circulates, a high water temperature cycle 4 in which cooling water circulates, a power module cycle 5 in which cooling water circulates, and a controller 10 that controls valve operations and the like in each cycle. It consists of. The cooling water is composed of, for example, an antifreeze. The vehicle air conditioner 1 is a heat pump system capable of cooling and heating.

  The refrigeration cycle 2 includes a compressor 20, a condenser 21, a water-refrigerant heat exchanger 22, an outdoor heat exchanger 23, an evaporator 24, a first three-way valve 25, a first on-off valve 26, and a first expansion. It comprises a valve 27, a second expansion valve 28, an accumulator 29, and a refrigerant flow path 30 connecting them so that the refrigerant can circulate.

  The compressor 20 pressurizes the gaseous refrigerant. As a result, the refrigerant becomes a high-temperature, high-pressure gas.

  The condenser 21 performs heat exchange between the refrigerant and the cooling water circulating in the high water temperature cycle 4 during heating, and transfers the heat of the refrigerant to the cooling water.

  The water-refrigerant heat exchanger 22 is provided in a second radiator tank 52 c of the power module cycle 5 described later, and performs heat exchange between the cooling water circulating in the power module cycle 5 and the refrigerant. The water-refrigerant heat exchanger 22 functions as a condenser during cooling, and functions as an evaporator during heating.

  The outdoor heat exchanger 23 is disposed in an engine room (a motor room in an electric vehicle) and performs heat exchange between the refrigerant that has passed through the water-refrigerant heat exchanger 22 and the outside air. The outdoor heat exchanger 23 functions as a condenser during cooling, and functions as an evaporator during heating.

  The evaporator 24 is disposed in the air passage 6 and performs heat exchange between the refrigerant decompressed and injected by the first expansion valve 27 and the air flowing through the air passage 6, and the air is evaporated when the refrigerant evaporates. Cooling. The air cooled by the evaporator 24 is used for in-vehicle air conditioning during cooling (dehumidification).

  The first three-way valve 25 switches the flow direction of the refrigerant that has passed through the outdoor heat exchanger 23. By switching the flow direction of the refrigerant by the first three-way valve 25, the refrigerant flows to the evaporator 24 via the first expansion valve 27 or flows by bypassing the evaporator 24.

  The accumulator 29 temporarily stores the refrigerant and supplies only the gaseous refrigerant to the compressor 20.

  The first on-off valve 26 is provided in the refrigerant flow path 30 that bypasses the capacitor 21 and the second expansion valve 28. When the first on-off valve 26 is closed, the refrigerant flows through the capacitor 21 and the second expansion valve 28. When the first on-off valve 26 is opened, the refrigerant flows bypassing the capacitor 21 and the second expansion valve 28.

  The high water temperature cycle 4 includes a first water pump 40, a heater 41, a condenser 21, a heater core 42, and a cooling water flow path 43 that connects them so that the cooling water can be circulated.

  The heater 41 generates heat by power supplied from a battery (not shown) and heats the cooling water.

  The heater core 42 is disposed in the air passage 6 and heats the air by exchanging heat between the cooling water heated by the heater 41 and the condenser 21 and the air around the heater core 42. The air heated by the heater core 42 is used for in-vehicle air conditioning during heating. When heating is OFF, the air mix door 7 prevents air from hitting the heater core 42 and prevents the air from being heated. A bypass passage may be provided so as to bypass the heater core 42.

  Next, the power module cycle 5 will be described with reference to FIGS. FIG. 2 is a block diagram of the power module cycle 5. FIG. 3 is a schematic view of the radiator 52. In FIG. 3, the flow of cooling water during heating is indicated by arrows.

  The power module cycle 5 includes a second water pump 50, a cooler 51, a radiator 52, a second on-off valve 56, and a cooling water passage 57 formed so that cooling water circulates through these. .

  The cooler 51 cools the power module and the battery that generate heat when the inverter or the motor is operated with cooling water.

  The radiator 52 includes a core portion 52a, a first radiator tank 52b, and a second radiator tank 52c. The radiator 52 is disposed in the engine room and is disposed side by side with the outdoor heat exchanger 23 in the vehicle width direction. That is, the radiator 52 and the outdoor heat exchanger 23 are disposed so as to be at substantially the same position in the vehicle front-rear direction.

  The first radiator tank 52b is connected to one end of the core portion 52a. In the first radiator tank 52b, a cooling water inlet 61c is formed at the lower part on the lower side in the vertical direction.

  The second radiator tank 52c is connected to the other end of the core portion 52a. As shown in FIG. 3, the second radiator tank 52 c is a double pipe in which the water-refrigerant heat exchanger 22 is disposed. In the second radiator tank 52 c, the refrigerant circulating in the refrigeration cycle 2 flows in the water-refrigerant heat exchanger 22, and the cooling water circulating in the power module cycle 5 flows outside the water-refrigerant heat exchanger 22.

  As shown in FIG. 3, the second radiator tank 52c has a refrigerant inlet 60a, a refrigerant outlet 60b, a heating cooling water inlet 61a, and a heating water inlet 61a so that the refrigerant flow direction and the cooling water flow direction are opposite to each other. A cooling water discharge port 61b is formed. Specifically, the refrigerant inlet 60a is formed vertically above the refrigerant outlet 60b, and the heating cooling water inlet 61a is formed vertically below the cooling water outlet 61b. In the second radiator tank 52c, the water-refrigerant heat exchanger 22 is disposed between the heating-time cooling water inlet 61a and the cooling water outlet 61b. In the water-refrigerant heat exchanger 22, the refrigerant of the refrigeration cycle 2 flows from the refrigerant introduction port 60a, and the refrigerant is discharged from the refrigerant discharge port 60b.

  In the second radiator tank 52c, a cooling water introduction port 61a is formed in the lower portion on the lower side in the vertical direction, and a cooling water discharge port 61b is formed in the upper portion on the upper side in the vertical direction. Further, the cooling water discharge port 61b is formed at a position diagonal to the cooling time cooling water introduction port 61c of the first radiator tank 52b. The heating cooling water inlet 61a is formed at a position that is substantially the same height as the cooling cooling water inlet 61c.

  The core portion 52a is formed by arranging a plurality of tubes in parallel and providing fins between the tubes. One end of each tube communicates with the first radiator tank 52b, and the other end communicates with the second radiator tank 52c. The flow passage cross-sectional area of the tube is smaller than the cross-sectional area of the second radiator tank 52c, and the water flow resistance of the core portion 52a is larger than the water flow resistance of the second radiator tank 52c.

  In the radiator 52, the diameter of the cooling water inlet 61c during cooling is smaller than the diameter of the cooling water inlet 61a during heating, and the water passage resistance of the core 52a is larger than the water passage resistance of the second radiator tank 52c. Further, the cooling water inlet 61c is formed in the lower part of the first radiator tank 52b, and the cooling water outlet 61b is formed in the upper part of the second radiator tank 52c, so that the cooling water is supplied from the cooling water inlet 61c. The flow path to the discharge port 61b is long. In this way, in the radiator 52, the water flow resistance from the cooling-time cooling water introduction port 61c to the core portion 52a causes the water flow of the second radiator tank 52c from the heating-time cooling water introduction port 61a to the cooling water discharge port 61b. It is larger than the resistance.

  In the power module cycle 5, it is the cooling water flow path 57 between the cooler 51 and the cooling water inlet 61a for heating, and the second cooling water flow path 57b (FIG. 5B) for flowing the cooling water into the second radiator tank 52c during heating. A second on-off valve 56 is provided. Further, the second radiator tank 52c is bypassed from the cooling water flow path 57 between the cooler 51 and the second on-off valve 56, and is connected to the core portion 52a via the first radiator tank 52b, and the first radiator is used during cooling. The cooling water flow path that forms the first cooling water flow path 57a (see FIG. 5) through which the cooling water flows into the tank 52b is branched.

  The second on-off valve 56 switches the inflow direction of the cooling water with respect to the radiator 52. When the second on-off valve 56 is open, the cooling water mainly flows into the second radiator tank 52c from the heating-time cooling water inlet 61a, and when the second on-off valve 56 is closed, the cooling water is supplied. Flows into the first radiator tank 52b from the cooling water inlet 61c.

  For example, the controller 10 controls the first three-way valve 25, the compressor 20, and the like according to the operation of the passenger.

  Next, the operation of the first embodiment will be described.

[When cooling]
During cooling, in the refrigeration cycle 2, as shown in FIG. 4A, the compressor 20, the first on-off valve 26, the water-refrigerant heat exchanger 22, the outdoor heat exchanger 23, the first three-way valve 25, the first expansion valve 27, The first on-off valve 26 and the first three-way valve 25 are controlled so that the first refrigerant flow path 30a through which the refrigerant flows in the order of the evaporator 24 and the accumulator 29 is formed. In FIG. 4A, the flow path through which the refrigerant or the cooling water flows is indicated by a solid line, and the flow path through which the refrigerant and the cooling water do not flow is indicated by a broken line. The refrigerant compressed by the compressor 20 and having a high temperature exchanges heat with the cooling water and the air around the outdoor heat exchanger 23 in the water-refrigerant heat exchanger 22. During cooling, the water-refrigerant heat exchanger 22 and the outdoor heat exchanger 23 function as a condenser, and the water-refrigerant heat exchanger 22 and the outdoor heat exchanger 23 condense the refrigerant and further supercool it. The Thereafter, the refrigerant is decompressed by the first expansion valve 27, and evaporates by exchanging heat with the air flowing through the air passage 6 in the evaporator 24. At that time, the air flowing through the air passage 6 is cooled, and this air is blown out into the passenger compartment.

  In the high water temperature cycle 4, the first water pump 40 is stopped and the cooling water does not circulate. The air mix door 7 prevents the air in the air path 6 from hitting the heater core 42.

  In the power module cycle 5, the second on-off valve 56 is closed. As a result, in the power module cycle 5, as shown in FIG. 5A, the first cooling water flows in the order of the second water pump 50, the cooler 51, the first radiator tank 52b, the core portion 52a, and the second radiator tank 52c. A water channel 57a is formed. In FIG. 5A, the 1st cooling water flow path 57a into which a cooling water flows is shown as a continuous line, and the cooling water flow path 57 into which a cooling water does not flow is shown with a broken line. The cooling water whose temperature has been increased by cooling the power module or the like by the cooler 51 first flows into the first radiator tank 52b and is cooled by exchanging heat with air by the core portion 52a. Thereafter, the cooling water flows into the second radiator tank 52c, performs heat exchange with the refrigerant of the refrigeration cycle 2 in the water-refrigerant heat exchanger 22, and cools the refrigerant.

  In the radiator 52, cooling water flows in from the cooling-time cooling water inlet 61c of the first radiator tank 52b located on the lower side in the vertical direction, and cools from the cooling water discharge port 61b of the second radiator tank 52c located on the upper side in the vertical direction. Water is discharged. Thereby, cooling water flows also to the tube of the core part 52a located in the vertical direction upper side, and cooling water can be poured over the core part 52a whole. That is, it is possible to prevent the cooling water from flowing unevenly in the core portion 52a. Further, in the second radiator tank 52c, a flow of cooling water from the lower side in the vertical direction to the upper side is generated, and the heat radiation amount of the refrigerant in the water-refrigerant heat exchanger 22 is increased.

  Thus, at the time of cooling, the cooling water cooled by the core portion 52a and having a low temperature is caused to flow into the second radiator tank 52c, thereby increasing the heat radiation amount of the refrigerant in the water-refrigerant heat exchanger 22. it can. That is, in the water-refrigerant heat exchanger 22, the condensation of the refrigerant can be promoted or the condensed refrigerant can be supercooled, so that the cooling efficiency of the refrigeration cycle 2 can be improved.

[When heating]
During heating, in the refrigeration cycle 2, as shown in FIG. 4B, the compressor 20, the condenser 21, the second expansion valve 28, the water-refrigerant heat exchanger 22, the outdoor heat exchanger 23, the first three-way valve 25, and the accumulator 29 The first on-off valve 26 and the first three-way valve 25 are controlled so that the second refrigerant flow path 30b through which the refrigerant flows in order is formed. The refrigerant which has been compressed by the compressor 20 and has a high temperature exchanges heat with the cooling water circulating in the high water temperature cycle 4 by the condenser 21. Thereby, the refrigerant is condensed, while the cooling water is heated. Thereafter, the refrigerant is decompressed by the second expansion valve 28 and introduced into the water-refrigerant heat exchanger 22. When the refrigerant passes through the water-refrigerant heat exchanger 22 and the outdoor heat exchanger 23, the refrigerant absorbs heat from the cooling water circulating in the power module cycle 5 and the air around the outdoor heat exchanger 23 and evaporates. That is, at the time of heating, the water-refrigerant heat exchanger 22 and the outdoor heat exchanger 23 function as an evaporator.

  In the high water temperature cycle 4, the cooling water circulated by the first water pump 40 is heated by the condenser 21, and the heated cooling water and the air flowing through the air passage 6 exchange heat with the heater core 42. Thereby, the air which flows through the air path 6 is heated, and warm air is blown out into a vehicle interior. If the air blown into the passenger compartment cannot be heated to a desired temperature only by heat exchange in the condenser 21, the cooling water is heated by the heater 41.

  In the power module cycle 5, the second on-off valve 56 is opened. As a result, both the first cooling water flow path 57a and the second cooling water flow path 57b are opened, but the cooling water introduction port 61c located downstream of the first cooling water flow path 57a leads to the core portion 52a. Since the water resistance is larger than the water flow resistance of the second radiator tank 52c from the cooling water introduction port 61a downstream of the second cooling water flow path 57b to the cooling water discharge port 61b, most of the cooling water is as shown in FIG. As shown, the second water pump 50, the cooler 51, the second on-off valve 56, and the second radiator tank 52c flow in this order. In FIG. 5B, the 2nd cooling water flow path 57b through which many cooling water flows is shown as a continuous line, and the cooling water flow path 57 where a cooling water does not flow or there are few flow rates is shown with a broken line. In this way, when the cooling water flows by bypassing the core portion 52a, when the waste heat of the power module recovered by the cooler 51 is to be used effectively for indoor heating, heat loss to the outside air is prevented. Can do.

  Incidentally, the water flow resistance from the cooling-time cooling water introduction port 61c to the core portion 52a is larger than the water flow resistance of the second radiator tank 52c from the heating-time cooling water introduction port 61a to the cooling water discharge port 61b. The flow path cross-sectional area in the core part 52a is small, and the flow path length from the cooling water inlet 61c to the cooling water outlet 61b is the flow from the cooling water inlet 61a to the cooling water outlet 61b. This is based on being longer than the path length and the diameter of the cooling water inlet 61c during cooling being smaller than the diameter of the cooling water inlet 61a during heating.

  During heating, heat is exchanged in the cooler 51 of the power module cycle 5 and the cooling water whose temperature has been increased is caused to flow into the second radiator tank 52c, and the water-refrigerant heat exchanger 22 absorbs heat from the refrigerant in the refrigeration cycle 2. And heat from the power module etc. is used for heating. Thereby, the heating efficiency of the refrigerating cycle 2 can be improved.

  The effect of 1st Embodiment of this invention is demonstrated.

  A cooling water inlet 61c for cooling is formed in the first radiator tank 52b of the radiator 52, a cooling water inlet 61a and a cooling water outlet 61b for heating are formed in the second radiator tank 52c, and the inside of the second radiator tank 52c is formed. The water-refrigerant heat exchanger 22 of the refrigeration cycle 2 is provided. During heating, cooling water having a high temperature is caused to flow into the second radiator tank 52c from the heating water inlet 61a formed in the second radiator tank 52c. Thereby, inflow of the cooling water to the core part 52a can be suppressed, a heat dissipation loss to the outside air of the cooling water can be prevented, the heat absorption amount of the refrigerant in the water-refrigerant heat exchanger 22 is increased, and the refrigeration cycle 2 Heating efficiency can be improved. Further, at the time of cooling, cooling water is introduced from a cooling-time cooling water inlet 61c formed in the first radiator tank 52b, and the cooling water cooled by the core portion 52a is caused to flow into the second radiator tank 52c. Thereby, the heat dissipation amount of the refrigerant in the water-refrigerant heat exchanger 22 is increased, and the cooling efficiency of the refrigeration cycle 2 can be improved.

  When the water-refrigerant heat exchanger 22 functions as an evaporator during heating and functions as a condenser during cooling, the vehicle air conditioner 1 can be downsized.

  In the second radiator tank 52c, the water-refrigerant heat exchanger 22 is provided between the heating-time cooling water inlet 61a and the cooling water outlet 61b. Thereby, the amount of heat exchange between the cooling water and the refrigerant at the time of heating and cooling can be increased, and the heating efficiency and the cooling efficiency can be improved.

  The cooling water inlet 61c is formed in the lower part of the first radiator tank 52b, and the cooling water outlet 61b is formed in the upper part of the second radiator tank 52c. Thereby, cooling water flows also into the tube of the core part 52a located in the vertical direction upper part at the time of cooling, can flow cooling water to the whole core part 52a at the time of cooling, and the cooling efficiency of the cooling water in the core part 52a is improved. Can be made. In addition, in the second radiator tank 52c, a flow from the lower side in the vertical direction toward the upper side is generated, and the heat radiation amount of the refrigerant in the water-refrigerant heat exchanger 22 is increased, so that the cooling efficiency can be improved.

  The diameter of the cooling water inlet 61c during cooling is made smaller than the diameter of the cooling water inlet 61a during heating. Further, the cooling water inlet 61c is formed in the lower part of the first radiator tank 52b, and the cooling water outlet 61b is formed in the upper part of the second radiator tank 52c, so that the cooling water is supplied from the cooling water inlet 61c. The flow path to the discharge port 61b is lengthened. In this manner, the water flow resistance from the cooling-time cooling water introduction port 61c to the core portion 52a is made larger than the water flow resistance from the heating-time cooling water introduction port 61a to the cooling water discharge port 61b. Thereby, it is possible to suppress the cooling water from flowing into the first radiator tank 52b during heating, to increase the flow rate of the cooling water flowing into the second radiator tank 52c, and the water-refrigerant heat exchanger 22 can be increased. The amount of heat absorbed by the refrigerant can be increased, and the heating efficiency can be improved.

  Next, a second embodiment of the present invention will be described with reference to FIGS. Here, a different part from 1st Embodiment is demonstrated and description is abbreviate | omitted about the same structure as 1st Embodiment. FIG. 6 is a block diagram of the power module cycle 5 of the second embodiment. FIG. 7 is a schematic view of the radiator 52 of the second embodiment. In FIG. 7, the flow of cooling water during heating is indicated by arrows.

  The power module cycle 5 includes a second water pump 50, a cooler 51, a radiator 52, a third on-off valve 58, and a cooling water passage 59 formed so that cooling water circulates through these. .

  In the first radiator tank 52b of the radiator 52, a cooling water discharge port 62c is formed at the upper part on the upper side in the vertical direction.

  As shown in FIG. 7, the second radiator tank 52c of the radiator 52 has a refrigerant introduction port 60a, a refrigerant discharge port 60b, a cooling water introduction port 62a, and a cooling water flow direction so that the flow direction of the refrigerant and the flow direction of the cooling water face each other. A cooling water discharge port 62b is formed during heating. In the second radiator tank 52c, the water-refrigerant heat exchanger 22 is disposed between the cooling water inlet 62a and the heating cooling water outlet 62b.

  In the second radiator tank 52c, a cooling water introduction port 62a is formed in the lower part on the lower side in the vertical direction, and a heating water discharge port 62b is formed in the upper part on the upper side in the vertical direction. The cooling water inlet 62a is formed at a position diagonal to the cooling water outlet 62c of the first radiator tank 52b. Further, the heating-time cooling water discharge port 62b is formed at a position that is substantially the same height as the cooling-time cooling water discharge port 62c.

  In the radiator 52, the diameter of the cooling water discharge port 62c during cooling is smaller than the diameter of the cooling water discharge port 62b during heating, and the water flow resistance of the core portion 52a is larger than the water flow resistance of the second radiator tank 52c. Further, the cooling water inlet 62a is formed in the lower part of the second radiator tank 52c, and the cooling water discharge port 62c is formed in the upper part of the first radiator tank 52b, whereby the cooling water cooling water is supplied from the cooling water inlet 62a. The flow path to the discharge port 62c is long. In this way, in the radiator 52, the water flow resistance of the first radiator tank 52b from the cooling water discharge port 62c to the core portion 52a is the second resistance from the cooling water introduction port 62a to the heating cooling water discharge port 62b. It is provided so as to be larger than the water flow resistance of the radiator tank 52c.

  In the power module cycle 5, a third on-off valve is provided in the fourth cooling water passage 59b (see FIG. 8B), which is a cooling water passage 59 between the cooling water discharge port 62b for heating and the cooler 51, and through which the cooling water flows during heating. 58 is provided. Further, a third cooling water passage 59a (FIG. 5) is connected to the core portion 52a via the first radiator tank 52b to the cooling water passage 59 between the third on-off valve 58 and the cooler 51, and the cooling water flows through the cooling. The cooling water flow path forming 8A) joins.

  Next, the operation of the second embodiment will be described.

[When cooling]
During cooling, in the power module cycle 5, the third on-off valve 58 is closed. Thereby, in the power module cycle 5, as shown in FIG. 8A, the third cooling water flows in the order of the second water pump 50, the cooler 51, the second radiator tank 52c, the core portion 52a, and the first radiator tank 52b. A water channel 59a is formed. In FIG. 8A, the third cooling water channel 59a through which the cooling water flows is indicated by a solid line, and the cooling water channel 59 through which the cooling water does not flow is indicated by a broken line.

  In the radiator 52, the cooling water flows in from the cooling water introduction port 62a of the second radiator tank 52c located on the lower side in the vertical direction, and cooled from the cooling water discharge port 62c of the first radiator tank 52b located on the upper side in the vertical direction. Water is discharged. Thereby, cooling water flows also to the tube located in the vertical direction upper side of the core part 52a, and cooling water can be poured through the core part 52a whole. Further, in the second radiator tank 52c, a flow of cooling water from the lower side in the vertical direction to the upper side is generated, and the heat radiation amount of the refrigerant in the water-refrigerant heat exchanger 22 is increased.

[When heating]
During heating, the third open / close valve 58 is opened in the power module cycle 5. As a result, in the power module cycle 5, both the third cooling water flow path 59a and the fourth cooling water flow path 59b are opened, but cooling during cooling from the core portion 52a upstream of the third cooling water flow path 59a. The water flow resistance reaching the water discharge port 62c is greater than the water flow resistance of the second radiator tank 52c from the cooling water introduction port 62a upstream of the fourth cooling water flow path 59b to the cooling water discharge port 62b during heating. Most of the cooling water flows in the order of the second water pump 50, the cooler 51, the second radiator tank 52c, and the third on-off valve 58, as shown in FIG. 8B. In FIG. 8B, the fourth cooling water flow path 59b through which a large amount of cooling water flows is indicated by a solid line, and the cooling water flow path 57 at which the cooling water does not flow or the flow rate is low is indicated by a broken line.

  Next, effects of the second embodiment will be described.

  The cooling water inlet 62a is formed in the lower part of the second radiator tank 52c, and the cooling water discharge outlet 62c is formed in the upper part of the first radiator tank 52b. Thereby, cooling water flows also into the tube of the core part 52a located in the vertical direction upper part at the time of cooling, can flow cooling water to the whole core part 52a at the time of cooling, and the cooling efficiency of the cooling water in the core part 52a is improved. Can be made. In addition, in the second radiator tank 52c, a flow from the lower side in the vertical direction toward the upper side is generated, and the heat radiation amount of the refrigerant in the water-refrigerant heat exchanger 22 is increased, so that the cooling efficiency can be improved.

  The diameter of the cooling water discharge port 62c during cooling is made smaller than the diameter of the cooling water discharge port 62b during heating. Further, the cooling water discharge port 62c is formed in the upper part of the first radiator tank 52b, and the cooling water introduction port 62a is formed in the lower part of the second radiator tank 52c, whereby the cooling water cooling water is supplied from the cooling water introduction port 62a. The flow path to the discharge port 62c is lengthened. In this way, the water flow resistance from the core portion 52a to the cooling-time cooling water discharge port 62c is made larger than the water flow resistance from the cooling water introduction port 62a to the heating-time cooling water discharge port 62b. Thereby, the flow rate of the cooling water flowing into the core portion 52a during heating is reduced, and the cooling water discharged from the cooling water discharge port 62b during heating, that is, the flow rate of the cooling water flowing around the water-refrigerant heat exchanger 22 The amount of heat absorbed by the refrigerant in the water-refrigerant heat exchanger 22 can be increased, and the heating efficiency can be improved.

  During cooling, the cooling water of the power module cycle 5 flows through the water-refrigerant heat exchanger 22 and then the cooling water cooled by the core portion 52a flows into the cooling device 51. Therefore, the cooling water flowing through the cooling device 51 For example, a power module such as an inverter can be further cooled.

  The embodiment of the present invention has been described above. However, the above embodiment only shows a part of application examples of the present invention, and the technical scope of the present invention is limited to the specific configuration of the above embodiment. Absent.

  In the said embodiment, although the cooling water was used in the power module cycle 5, it is not limited to this, You may use a refrigerant | coolant and gas as a cooling medium.

  In the refrigeration cycle 2, the positions of the outdoor heat exchanger 23 and the water-refrigerant heat exchanger 22 may be reversed so that the refrigerant that has passed through the outdoor heat exchanger 23 flows into the water-refrigerant heat exchanger 22. May be.

  Further, when the refrigerant heated by the water-refrigerant heat exchanger 22 is cooled by passing through the outdoor heat exchanger 23 during heating, a flow path and a valve are provided so as to bypass the outdoor heat exchanger 23. It may be provided. Thereby, at the time of heating, it can prevent that the temperature of the refrigerant | coolant of the refrigerating cycle 2 becomes low, and can improve heating efficiency.

  Further, instead of the second on-off valve 56 of the first embodiment, a three-way valve may be provided at a branch point of the flow path. Thereby, it is possible to prevent the cooling water of the power module cycle 5 from flowing through the core portion 52a during heating, and it is possible to prevent the cooling water cooled by the core portion 52a from flowing into the second radiator tank 52c. The temperature of the cooling water flowing through the two radiator tank 52c can be increased. Thereby, the heat absorption amount of the water-refrigerant heat exchanger 22 can be increased, and the heating efficiency can be improved. Moreover, in the said embodiment, it may replace with the power module cycle 5, and may apply the cooling water cycle for battery (a fuel cell is included) temperature control.

  In the first embodiment, the cooling water inlet 61c for cooling is formed in the upper part of the first radiator tank 52b, the cooling water outlet 61b is formed in the lower part of the second radiator tank 52c, and the cooling water inlet 61a for heating is formed. You may form in the upper part of the 2nd radiator tank 52c. This also lengthens the flow path from the cooling water inlet 61c to the cooling water outlet 61b and increases the water flow resistance, and the cooling water flowing into the cooling water inlet 61c at the time of heating. , The heat absorption amount of the refrigerant in the water-refrigerant heat exchanger 22 can be increased, and the heating efficiency can be improved. In this case, the refrigerant introduction port 60a is formed above the refrigerant discharge port 60b in the vertical direction.

  In the second embodiment, the cooling water discharge port 62c for cooling is formed in the lower part of the first radiator tank 52b, the cooling water inlet 62a is formed in the upper part of the second radiator tank 52c, and the cooling water discharge port 62b for heating is formed. You may form in the lower part of the 2nd radiator tank 52c. This also lengthens the flow path from the cooling water introduction port 62a to the cooling water discharge port 62c during cooling, increases the water flow resistance, and reduces the flow rate of cooling water flowing into the core portion 52a during heating. And the heat absorption amount of the refrigerant | coolant in the water-refrigerant heat exchanger 22 can be enlarged, and heating efficiency can be improved. In this case, the refrigerant introduction port 60a is formed above the refrigerant discharge port 60b in the vertical direction.

DESCRIPTION OF SYMBOLS 1 Vehicle air conditioner 2 Refrigeration cycle 4 High water temperature cycle 5 Power module cycle 22 Water-refrigerant heat exchanger (heat exchange part)
52 Radiator (Composite Heat Exchanger)
52a 1st radiator tank (1st tank part)
52b Core part (heat dissipation part)
52c 2nd radiator tank (2nd tank part)
61a Cooling water inlet for heating (second inlet)
61b Cooling water outlet (second outlet)
61c Cooling water inlet (first inlet) during cooling
62a Cooling water inlet (second inlet)
62b Cooling water outlet for heating (second outlet)
62c Cooling water outlet for cooling (first outlet)

Claims (10)

A heat dissipating part that dissipates the heat of the cooling medium to the outside air;
A first tank connected to one end of the heat dissipating part and through which the cooling medium flows;
A second tank part connected to the other end of the heat dissipating part and through which the cooling medium flows;
A heat exchange unit provided in the second tank unit, in which a refrigerant of a refrigeration cycle flows, and the cooling medium and the refrigerant exchange heat;
The first tank portion is provided with only one of a first inflow portion into which the cooling medium can flow and a first discharge portion from which the cooling medium can be discharged,
The second tank portion is provided with a second inflow portion through which the cooling medium can flow and a second discharge portion through which the cooling medium can be discharged.
A combined heat exchanger characterized by that. The composite heat exchanger according to claim 1,
The heat exchange unit functions as a condenser during cooling and functions as an evaporator during heating.
A combined heat exchanger characterized by that. The composite heat exchanger according to claim 1 or 2,
The heat exchange part is provided between the second inflow part and the second discharge part.
A combined heat exchanger characterized by that. A composite heat exchanger according to any one of claims 1 to 3,
The water flow resistance from the first inflow part or the first discharge part to the heat radiating part is larger than the water flow resistance from the second inflow part to the second discharge part,
A combined heat exchanger characterized by that. A composite heat exchanger according to any one of claims 1 to 3,
The first inflow portion is provided at a lower portion of the first tank portion,
The second discharge part is provided in an upper part of the second tank part.
A combined heat exchanger characterized by that. A composite heat exchanger according to any one of claims 1 to 3,
The first inflow part is provided at an upper part of the first tank part,
The second discharge part is provided at a lower part of the second tank part;
A combined heat exchanger characterized by that. A composite heat exchanger according to any one of claims 1 to 3,
The first discharge part is provided on an upper part of the first tank part,
The second inflow portion is provided at a lower portion of the second tank portion;
A combined heat exchanger characterized by that. A composite heat exchanger according to any one of claims 1 to 3,
The first discharge part is provided at a lower part of the first tank part,
The second inflow portion is provided at a lower portion of the second tank portion;
A combined heat exchanger characterized by that. A composite heat exchanger according to any one of claims 1 to 3,
The first inflow portion has a smaller diameter than the second inflow portion.
A combined heat exchanger characterized by that. A composite heat exchanger according to any one of claims 1 to 3,
The first discharge part has a smaller diameter than the second discharge part,
A combined heat exchanger characterized by that.