WO2013084472A1 - Heat utilization system - Google Patents

Abstract

This heat utilization system is provided with a refrigerant circuit (10), auxiliary medium circuits (40, 60), and heat exchangers (70, 370, 470). The heat exchangers comprise: a plurality of refrigerant tubes (16a) that exchange heat between air and a refrigerant supplied by the refrigerant circuit; and a plurality of auxiliary medium tubes (43a) that exchange heat between the air and an auxiliary medium supplied by the auxiliary medium circuits. The refrigerant tubes and the auxiliary medium tubes are positioned in such a manner as to form a line in a direction (RD) that intersects the direction of flow (CD) of the air, and in at least part of the line, the refrigerant tubes and the auxiliary medium tubes are positioned so as to be able to transfer heat.

Description

Heat utilization system Cross-reference of related applications

This disclosure is based on Japanese Application No. 2011-269223 filed on December 8, 2011 and Japanese Application No. 2012-257786 filed on November 26, 2012. Incorporate.

The present disclosure relates to a heat utilization system that uses cold and / or heat. The present disclosure can be applied to, for example, a vehicle heat utilization system that supplies cold and warm heat in a vehicle.

Patent Document 1 discloses a vehicle heat pump cycle, which is one of heat utilization systems, and defrosting control of the evaporator. Patent Documents 2 to 7 disclose a heat exchanger capable of flowing a plurality of media.

In the prior art, the refrigerant supplied from the refrigeration cycle and the cooling water supplied from the heat generating device mounted on the vehicle are passed through the outdoor heat exchanger. For this reason, sufficient consideration is not paid about the case where both a refrigerant | coolant and cooling water are poured into a utilization side heat exchanger, for example, an indoor heat exchanger. Therefore, the prior art required improvement in application to the use side heat exchanger.

Japanese Patent Laid-Open No. 2008-221997 Japanese Utility Model Publication No. 63-154967 JP-A-8-258548 JP-A-11-157326 JP 2000-62446 A JP 2001-55036 A Japanese Patent No. 431115

An object of the present disclosure is to provide a heat utilization system using a heat exchanger capable of flowing a refrigerant supplied from a refrigeration cycle and an auxiliary medium.

Another object of the present disclosure is to provide a heat utilization system that can realize temperature adjustment of air to be used by a refrigerant supplied from a refrigeration cycle and an auxiliary medium.

Another object of the present disclosure is to provide a heat utilization system with good drainage of condensed water generated by a cooling action by a refrigerant or an auxiliary medium.

Still another object of the present disclosure is to provide a heat utilization system suitable for use of the heat exchanger proposed by the inventors in Japanese Patent Application No. 2011-144501, Japanese Patent Application No. 2011-123199, or Japanese Patent Application No. 2011-82760. It is to be.

This disclosure employs the following technical means in order to achieve the above object.

According to an example of the present disclosure, a heat utilization system includes a compressor that supplies a high-pressure refrigerant by sucking and compressing low-pressure refrigerant, a refrigerant circuit that includes a decompressor that depressurizes the high-pressure refrigerant and supplies low-pressure refrigerant, and a refrigerant Heat exchange between the auxiliary medium circuit, which is configured separately from the circuit, in which the auxiliary medium circulates, the auxiliary medium circuit in which the auxiliary medium for adjusting the temperature of the heat generating device circulates, and the refrigerant and use air supplied from the refrigerant circuit A plurality of refrigerant tubes, a utilization side heat exchanger having a plurality of auxiliary medium tubes for exchanging heat between the auxiliary medium supplied from the auxiliary medium circuit and the utilization air, and a control device for controlling the refrigerant circuit and the auxiliary medium circuit With. The refrigerant tube and the auxiliary medium tube are arranged in a row along a direction intersecting the flow direction of the utilization air, and the refrigerant tube and the auxiliary medium tube are heated in at least a part of the row. It is arranged to be able to communicate.

According to this configuration, heat exchange between the three parties is provided in the use side heat exchanger. One is heat exchange between the refrigerant in the refrigerant tube and the use air. One is heat exchange between the auxiliary medium in the auxiliary medium tube and the use air. Still another one is heat exchange between the auxiliary medium in the auxiliary medium tube and the refrigerant in the refrigerant tube. According to this structure, the temperature adjustment of the utilization air utilized can be implement | achieved with the refrigerant | coolant supplied from a refrigerant circuit, and an auxiliary | assistant medium.

For example, the auxiliary medium is a medium for adjusting the temperature of the heat generating device. According to this configuration, a medium for controlling the temperature of the heat generating device can be used.

For example, the use side heat exchanger includes fins arranged in an air passage formed between the refrigerant tube and the auxiliary medium tube, and the refrigerant tube and the auxiliary medium tube can transfer heat via the fins. . According to this configuration, heat exchange between the refrigerant tube and the use air can be promoted by the fins. Further, heat exchange between the auxiliary medium tube and the use air can be promoted by the fins. Furthermore, heat exchange between the refrigerant and the auxiliary medium is possible by heat transfer through the fins.

For example, the number of refrigerant tubes is larger than the number of auxiliary medium tubes. According to this configuration, a heat exchanger with relatively high heat exchange performance by the refrigerant tube is provided.

For example, the refrigerant tubes and the auxiliary medium tubes are arranged so as to constitute at least an upstream row and a downstream row with respect to the flow direction of the air used, and the refrigerant tubes are a majority in the upstream row. According to this configuration, the generation of condensed water can be biased to the upstream line.

For example, the refrigerant tubes and the auxiliary medium tubes are arranged so as to constitute at least an upstream row and a downstream row with respect to the flow direction of the use air, and the refrigerant tubes are a majority in the downstream row. According to this configuration, the generation of condensed water can be biased to the downstream line.

For example, the control device controls the refrigerant circuit and the auxiliary medium circuit so as to adjust the temperature of the auxiliary medium with the refrigerant. According to this configuration, the temperature of the auxiliary medium is adjusted by heat exchange between the refrigerant and the auxiliary medium. For example, when the temperature of the refrigerant is lower than the temperature of the auxiliary medium, the auxiliary medium can be cooled by the refrigerant. Further, when the temperature of the refrigerant is higher than the temperature of the auxiliary medium, the auxiliary medium can be heated by the refrigerant.

For example, in order to further adjust the amount of heat exchange between the refrigerant and the auxiliary medium, an air volume adjusting device for adjusting the flow rate of the air used is provided. According to this configuration, the amount of heat exchange between the refrigerant and the auxiliary medium can be adjusted by the flow rate of the utilization air. By reducing the flow rate of the use air, it is possible to increase the cooling amount of the auxiliary medium by the refrigerant or increase the heating amount of the auxiliary medium by the refrigerant.

For example, the control device controls the auxiliary medium circuit so as to cool the use air by the auxiliary medium. According to this configuration, the use air can be cooled by the auxiliary medium. As a result, use air can be cooled without depending only on the refrigerant circuit.

For example, the control device controls the auxiliary medium circuit so as to radiate heat from the auxiliary medium to the use air. According to this configuration, the auxiliary medium can be cooled by heat radiation from the auxiliary medium to the use air. Since the cooled auxiliary medium is supplied to the heat generating device, the heat generating device can be cooled by using the use air.

For example, the control device controls the flow rate of the refrigerant or the flow rate of the auxiliary medium in response to the adhesion of frost in the use side heat exchanger. According to this configuration, the flow rate of the refrigerant or the auxiliary medium is adjusted in response to the adhesion of frost in the use side heat exchanger. For example, when the refrigerant cools the use air, the control device decreases the refrigerant flow rate in response to the adhesion of frost. When the auxiliary medium is cooling the cooling air, the control device decreases the flow rate of the auxiliary medium. When the refrigerant cools the use air and the auxiliary medium heats the use air, the control device increases the flow rate of the auxiliary medium. When the refrigerant heats the use air and the auxiliary medium cools the use air, the control device increases the flow rate of the refrigerant.

For example, the refrigerant circuit supplies low-pressure refrigerant to the refrigerant tube. According to this configuration, cooling of the use air and cooling of the auxiliary medium can be provided by the low-pressure refrigerant.

For example, the auxiliary medium circuit includes an auxiliary medium heat exchanger that cools the auxiliary medium, and the auxiliary medium circuit cools the utilization air by supplying the auxiliary medium cooled by the auxiliary medium heat exchanger to the auxiliary medium tube. . According to this configuration, the use air can be cooled by the auxiliary medium.

For example, the refrigerant circuit includes an outdoor refrigerant heat exchanger that exchanges heat between the unused air and the low-pressure refrigerant and absorbs heat to the low-pressure refrigerant, and the auxiliary medium heat exchanger uses the low-pressure refrigerant or the unused air in the outdoor refrigerant heat exchanger. Cool the auxiliary medium. According to this configuration, the auxiliary medium can be cooled by the low temperature obtained in the outdoor refrigerant heat exchanger by the refrigerant circuit or the low temperature of the unused air.

For example, the refrigerant circuit includes a cycle switching device that switches a flow path between a heating application and a cooling application, and the outdoor refrigerant heat exchanger exchanges heat between unused air and low-pressure refrigerant in the heating application, and absorbs heat into the low-pressure refrigerant. In cooling applications, heat is exchanged between non-use air and high-pressure refrigerant to dissipate heat from the high-pressure refrigerant. According to this configuration, the refrigerant circuit can be used by switching between a heating application and a cooling application. Outdoor refrigerant heat exchangers are used as heat absorbers in heating applications, and are used as radiators in cooling applications.

For example, the control device assists by increasing the flow rate of the auxiliary medium flowing to the auxiliary medium heat exchanger according to the performance degradation due to frost in the outdoor refrigerant heat exchanger or increasing the heat load of the use side heat exchanger. Increase the amount of heat given to the medium heat exchanger. According to this structure, the performance fall resulting from the frost adhering to an outdoor refrigerant | coolant heat exchanger can be compensated.

For example, a temperature sensor for detecting the temperature in the use side heat exchanger is further provided, and the control device controls the refrigerant circuit in the cooling application based on the temperature detected by the temperature sensor and cools based on the temperature detected by the temperature sensor. Control the water circuit. According to this configuration, the temperature sensor for controlling the refrigerant circuit can be used for controlling the cooling water circuit.

For example, it further includes a non-use side heat exchanger having a plurality of tubes arranged in a row along a direction intersecting the flow direction of non-use air, and the tubes are supplied from the refrigerant circuit. Multiple refrigerant tubes that exchange heat between low-pressure refrigerant and unused air, and heat exchange between auxiliary medium and unused air supplied from the auxiliary medium circuit, so that heat can be transferred to the refrigerant tubes in at least a part of the row A plurality of auxiliary media tubes are disposed. According to this configuration, the heat exchanger that exchanges heat between the refrigerant, the auxiliary medium, and the unused air is also used for the unused heat exchanger.

For example, the apparatus further includes a use-side heat exchanger for high-pressure refrigerant having a plurality of tubes arranged in a row along a direction intersecting the flow direction of the use air, and the tubes are supplied from the refrigerant circuit. A plurality of refrigerant tubes for exchanging heat between the high-pressure refrigerant to be used and the used air, and heat exchange between the auxiliary medium and the used air supplied from the auxiliary medium circuit so that heat can be transferred to the refrigerant tubes in at least a part of the row. A plurality of auxiliary media tubes are disposed. According to this structure, the heat exchanger which heat-exchanges a refrigerant | coolant, an auxiliary | assistant medium, and utilization air is used also for the utilization side heat exchanger for a heating.

For example, the refrigerant circuit supplies high-pressure refrigerant to the refrigerant tube. According to this configuration, heating of the utilization air and heating of the auxiliary medium can be provided by the high-pressure refrigerant.

For example, the air used is air for air conditioning. According to this configuration, it is possible to provide air conditioning and temperature adjustment of the heat generating device.

For example, the air used is the air in the cabinet that can accommodate the goods. According to this structure, temperature control of the articles | goods in a store | warehouse | chamber and temperature control of a heat-emitting device can be provided.

For example, after the power becomes available, the control device executes temperature control of the heat generating device by the auxiliary medium circuit in preference to temperature control of the use air by the use side heat exchanger. According to this configuration, priority is given to the temperature control of the heat generating device, and then the temperature control of the use air is executed.

For example, the utilization device includes a battery charged by an external power source, and the control device controls the temperature of the battery by the auxiliary medium circuit in preference to the temperature control of the utilization air by the utilization side heat exchanger when the battery is charged. Execute. According to this configuration, priority is given to the temperature control of the battery, and then the temperature control of the use air is executed.

In addition, the code | symbol in the parenthesis described in the claim shows the correspondence with the specific means as described in embodiment mentioned later as one aspect, Comprising: The technical scope of this indication is limited is not.

It is a block diagram showing the air-conditioner of a 1st embodiment of this indication. It is a perspective view of the heat exchanger of a 1st embodiment. It is a disassembled perspective view of the heat exchanger of 1st Embodiment. FIG. 4 is a partial cross-sectional view of the heat exchanger in the IV-IV cross section of FIG. 2. 1 is a simplified exploded perspective view of a heat exchanger according to a first embodiment. FIG. 4 is a partial cross-sectional view of the heat exchanger in the VI-VI cross section of FIG. It is a disassembled perspective view of the heat exchanger of 2nd Embodiment of this indication. It is a fragmentary sectional view of the heat exchanger of a 2nd embodiment. It is a disassembled perspective view of the heat exchanger of 3rd Embodiment of this indication. It is a fragmentary sectional view of the heat exchanger of a 4th embodiment of this indication. It is a fragmentary sectional view of the heat exchanger of a 5th embodiment of this indication. It is a fragmentary sectional view of the heat exchanger of a 6th embodiment of this indication. It is a fragmentary sectional view of the heat exchanger of a 7th embodiment of this indication. It is a block diagram showing an air-conditioner of an 8th embodiment of this indication. It is a block diagram showing an air conditioner of a 9th embodiment of this indication. It is a block diagram showing an air-conditioner of a 10th embodiment of this indication. It is a block diagram showing an air-conditioner of an 11th embodiment of this indication. It is a block diagram showing an air-conditioner of a 12th embodiment of the present disclosure. It is a fragmentary sectional view of the heat exchanger of a 13th embodiment of this indication. FIG. 20 is a transition diagram of condensed water in the section XX-XX in FIG. 19. FIG. 20 is a transition diagram of condensed water in the XXI-XXI cross section of FIG. 19. It is a fragmentary sectional view of the heat exchanger of a comparative example. FIG. 23 is a transition diagram of condensed water in the section XXIII-XXIII in FIG. 16 is a flowchart of a fourteenth embodiment of the present disclosure. 19 is a flowchart according to a fifteenth embodiment of the present disclosure.

Hereinafter, a plurality of modes for carrying out the invention will be described with reference to the drawings. In each embodiment, parts corresponding to the matters described in the preceding embodiment may be denoted by the same reference numerals, and redundant description may be omitted. When only a part of the configuration is described in each mode, the other modes described above can be applied to the other parts of the configuration. Further, in the following embodiments, the correspondence corresponding to the matters corresponding to the matters described in the preceding embodiments is indicated by adding reference numerals that differ only by one hundred or more, and redundant description may be omitted. . Not only combinations of parts that clearly show that combinations are possible in each embodiment, but also combinations of the embodiments even if they are not explicitly stated unless there is a problem with the combination. Is also possible.

(First embodiment)
In FIG. 1, an embodiment of the present disclosure provides a vehicle air conditioner 1 that shows an example of a vehicle heat utilization system. The air conditioner 1 includes a refrigerant circuit 10 constituting a refrigeration cycle for cooling. The air conditioner 1 includes a heat exchanger 70 to which the disclosed invention is applied. A cooling water circuit 40 for adjusting the temperature of the heat source HS mounted on the vehicle is mounted on the vehicle. The refrigerant circuit 10 and the coolant circuit 40 are thermally related via the heat exchanger 70.

The air conditioner 1 is adapted to a so-called hybrid vehicle that obtains driving power from an internal combustion engine (engine) and a motor generator. The air conditioner 1 can be used for any of a vehicle using only an engine as a power source, a hybrid vehicle, and a vehicle using only an electric motor as a power source.

The air conditioner 1 provides cooling by cold heat supplied by the refrigerant circuit 2. The air conditioner 1 includes an air conditioning unit 30 that blows air UR toward a vehicle interior that is an air conditioning target space. In this embodiment, utilization air is the air UR for an air conditioning. The air conditioner 1 includes a refrigerant circuit 10, a cooling water circuit 40, and a control device (CNTR) 100 that controls the air conditioning unit 30.

The control device 100 is provided by a microcomputer provided with a computer-readable storage medium. The storage medium stores a computer-readable program non-temporarily. The storage medium can be provided by a semiconductor memory or a magnetic disk. The program is executed by the control device 100 to cause the control device 100 to function as a device described in this specification, and to cause the control device 100 to function so as to execute the control method described in this specification. The means provided by the control device 100 can also be referred to as a functional block or module that achieves a predetermined function.

The control device 100 controls the operation of the devices 11, 17, and 41. The control device 100, the refrigerant circuit 10, and the cooling water circuit 40 are controlled. A plurality of sensors are connected to the control device 100. The control device 100 provides control means for controlling the amount of refrigerant flowing through the refrigerant circuit 10. The amount of refrigerant is controlled by adjusting the refrigerant discharge capacity of the compressor 11. Moreover, the control apparatus 100 provides the control means which controls the flow of the cooling water in a cooling water circuit, and a flow path. The flow of the cooling water is controlled by controlling the pump 41. The control device 100 controls the cooling water circuit 40 so that the temperature of the cooling water WT falls below a predetermined upper limit temperature and exceeds a predetermined lower limit temperature.

The air conditioning unit 30 is arranged in the passenger compartment. The air conditioning unit 30 includes a casing 31 that provides a duct for the air UR sent toward the passenger compartment. The air conditioning unit 30 is configured by arranging components such as the blower 32, the heater core 12, and the indoor heat exchanger 20 in a casing 31. An inside / outside air switching device 33 that introduces air in the passenger compartment and air outside the passenger compartment selectively or in a mixed manner is disposed at the most upstream portion in the casing 31. A blower 32 for blowing air UR is disposed on the downstream side of the inside / outside air switching device 33.

At the downstream side of the blower 32, the indoor heat exchanger 20 and the heater core 12 are arranged in this order with respect to the flow of the air UR. The indoor heat exchanger 20 is disposed on the upstream side with respect to the heater core 12. The indoor heat exchanger 20 includes a refrigerant heat exchanger 16 that exchanges heat between the refrigerant RF and the air UR. The refrigerant heat exchanger 16 can also be referred to as an evaporator 16. The refrigerant heat exchanger 16 is a cooling heat exchanger that cools the air UR by exchanging heat between the refrigerant RF and the air UR flowing through the refrigerant heat exchanger 16. The refrigerant heat exchanger 16 is also a use-side heat exchanger for low-pressure refrigerant for using the cold supplied by the refrigerant RF flowing through the refrigerant circuit 10 for cooling the air UR. The heater core 12 is a heat exchanger for heating that heats the air UR with the cooling water WT flowing inside the heater core 12 or an electric heater.

The air mix door 34 is disposed on the downstream side of the indoor heat exchanger 20 and on the upstream side of the heater core 12. The air mix door 34 adjusts the ratio of passing through the heater core 12 in the air UR after passing through the indoor heat exchanger 20. A mixing chamber 35 is provided on the downstream side of the heater core 12. The mixing chamber 35 mixes the air UR heated by the heater core 12 and the air UR that bypasses the heater core 12 and is not heated. The downstream of the mixing chamber 35 communicates with the vehicle interior via a blowout port.

The refrigerant circuit 10 is provided by a vapor compression refrigeration cycle. The refrigerant circuit 10 is a refrigerant cycle for cooling the air conditioner 1. The refrigerant circuit 10 is also called a refrigerant system. The refrigerant circuit 10 causes the refrigerant RF to flow through a refrigerant tube 16a described later, and takes heat from the air UR or the cooling water WT by evaporation of the refrigerant RF. The refrigerant circuit 10 supplies low-pressure refrigerant to the refrigerant tube 16a.

The compressor 11 is disposed in the engine room. The compressor 11 sucks low-pressure refrigerant in the refrigerant circuit 10 and compresses it to supply high-pressure refrigerant. The compressor 11 includes a compression mechanism 11a such as a scroll type or a vane type, and an electric motor 11b that drives the compression mechanism 11a. The electric motor 11b is controlled by the control device 100.

An outdoor heat exchanger 21 is provided on the discharge side of the compressor 11. The outdoor heat exchanger 21 is disposed in the engine room. The outdoor heat exchanger 21 is supplied with high-pressure refrigerant and radiates heat from the high-pressure refrigerant to the air AR. The air AR is outdoor air and is also called non-use air. The outdoor heat exchanger 21 is also called a condenser. A receiver tank 22 for storing excess refrigerant is provided downstream of the outdoor heat exchanger 21. The fan 17 is an electric blower. The fan 17 provides an outdoor blowing unit that blows the air AR toward the outdoor heat exchanger 21.

An expansion valve 19 for cooling is provided downstream of the receiver tank 22. The expansion valve 19 is a decompression unit. The expansion valve 19 provides a decompressor that decompresses the high-pressure refrigerant and supplies the low-pressure refrigerant. The decompressor can be provided by an orifice, a capillary tube, or the like. An indoor heat exchanger 20 is provided downstream of the expansion valve 19. Further, a compressor 11 is provided downstream of the indoor heat exchanger 20.

A temperature sensor 23 for detecting the occurrence of freezing on the indoor heat exchanger 20 is provided on the outdoor heat exchanger 20, that is, on the downstream side of the heat exchanger 70 or on the surface of the heat exchanger 70. The detection signal of the temperature sensor 23 is used to suppress a decrease in cooling performance due to frost on the surface of the indoor heat exchanger 20, that is, the heat exchanger 70. For example, when the temperature detected by the temperature sensor 23 falls below a predetermined threshold temperature, the flow rate of the refrigerant RF is reduced. Thereby, adhesion of excessive frost is suppressed. In this embodiment, the temperature sensor 23 is provided at a position where frost adhesion on the heat exchanger 70 is likely to appear in the temperature. The temperature sensor 23 can be provided in the vicinity of the heat exchanger 70 and downstream of the air UR.

The cooling water circuit 40 can flow cooling water WT used as a heat carrying medium and a heat storage medium. As the heat source HS, one of in-vehicle devices that generate heat during operation can be used. The heat source HS is provided by at least one of an engine of a hybrid vehicle, a motor generator, an inverter circuit, a battery, a control circuit, and the like. The heat source HS supplies heat to the cooling water WT. The heat source HS is a heat generating device mounted on the vehicle. The cooling water WT is an auxiliary medium for adjusting the temperature of the heat source HS. The cooling water circuit 40 is an auxiliary medium circuit that is configured separately from the refrigerant circuit and in which the auxiliary medium circulates. The cooling water circuit 40 is an auxiliary medium circuit in which an auxiliary medium for adjusting the temperature of the heat source HS circulates. The cooling water circuit 40 is also a cooling system for cooling the heat source HS and keeping it at an appropriate temperature. The cooling water circuit 40 including the heat source HS is called a water system or a heat generating equipment system. The coolant circuit 40 is a coolant circulation circuit that circulates the coolant WT through the heat source HS and cools the heat source HS. The cooling water circuit 40 includes components such as a pump 41 and a radiator 43.

The pump 41 is an electric pump that pumps cooling water to the cooling water circuit 40. The radiator 43 is disposed in the casing 31 together with the indoor heat exchanger 20. The radiator 43 is a heat dissipation heat exchanger that exchanges heat between the cooling water WT and the air UR. The radiator 43 is also called a cooling water heat exchanger 43 that exchanges heat between the cooling water WT for the heat source HS and the air UR. The pump 41 provides a flow rate regulator that regulates the flow rate of the cooling water WT supplied to the radiator 43.

The refrigerant heat exchanger 16 and the radiator 43 are integrally configured to constitute a heat exchanger 70. The heat exchanger 70 is a heat exchanger unit that can be handled as an integral unit. The refrigerant heat exchanger 16 and the radiator 43 can be disposed adjacent to each other. In the heat exchanger 70, the refrigerant heat exchanger 16 and the radiator 43 are thermally coupled. The refrigerant heat exchanger 16 and the radiator 43 can be configured by being closely coupled mechanically and thermally via a member excellent in heat conduction. Moreover, although the refrigerant | coolant heat exchanger 16 and the radiator 43 are mechanically couple | bonded via a member, they can be comprised so that it may couple | bond indirectly weakly via the air UR from a thermal viewpoint.

The air conditioner 1 includes a cooling water circuit 60 that supplies hot water to the heater core 12. The cooling water circuit 60 is a temperature adjustment circuit that cools the heat source HS such as an engine with a medium such as cooling water. The cooling water circuit 60 can include a pump 61 for flowing the cooling water WT.

The cooling water circuit 60 and the cooling water circuit 40 can be independent circuits that use different heat sources HS. For example, the heat source HS of the coolant circuit 60 can be an engine, and the heat source HS of the coolant circuit 40 can be an electrical device. The cooling water circuit 60 and the cooling water circuit 40 can be provided by a common cooling water circuit. For example, the radiator 43 and the heater core 12 can be arranged in parallel or in series in the cooling water circuit 40.

In FIG. 2, a heat exchanger 70 is a so-called tank and tube type heat exchanger. Air UR is supplied to the core portion 71 of the heat exchanger 70. The air UR flows through the core portion 71. The core portion 71 is formed in a thin plate shape having an upstream surface as an inlet side and a downstream surface as an outlet side with respect to the flow of the air UR. The heat exchanger 70 provides heat exchange between the three of the refrigerant RF, the cooling water WT, and the air UR. The heat exchanger 70 provides heat exchange between the refrigerant RF and the cooling water WT, between the refrigerant RF and the air UR, and between the cooling water WT and the air UR.

The refrigerant tube 16a and the water tube 43a are arranged in a line along a direction RD that intersects the flow direction CD of the air UR. Furthermore, the refrigerant | coolant tube 16a and the water tube 43a are arrange | positioned in at least one part of a row | line | column so that heat transfer is possible. The plurality of tubes 16a and 43a are arranged in a row along a direction orthogonal to the flow direction of the air UR. In the figure, the column direction RD, the row direction CD, and the length direction LD of the tubes 16a and 43a are shown. The column direction RD is also called a height direction or a width direction. The column direction RD is also the length direction of the tank portions 72 and 75. The row direction CD is also called a depth direction or a thickness direction. The row direction CD is also the flow direction of the air UR.

2 to 6, the heat exchanger 70 is arranged in a plurality of tubes 16a for circulating the refrigerant RF, a plurality of tubes 43a for circulating the cooling water WT, and air passages 16b, 43b between the plurality of tubes 16a, 43a. And a plurality of fins 50 and parts such as a collection tank and a distribution tank disposed at both ends of the plurality of tubes. The heat exchanger 70 has components as the refrigerant heat exchanger 16 and components as the radiator 43. Those parts are thermally coupled.

The heat exchanger 70 includes a core part 71 and tank parts 72 and 75. In the core part 71, the several tubes 16a and 43a are arrange | positioned so that heat exchange with the air UR is possible. The plurality of tubes 16a and 43a include a plurality of refrigerant tubes 16a for the refrigerant supplied from the refrigeration cycle. Furthermore, the plurality of tubes 16a and 43a include a plurality of water tubes 43a for the cooling water WT for adjusting the temperature of the heat source HS mounted on the vehicle. The tank parts 72 and 75 are provided at both ends of the core part 71. Each of the tank portions 72 and 75 includes water tanks 73 and 77 and refrigerant tanks 74 and 76. The water tank 73 and the refrigerant tank 76 are also called outer tanks 73 and 76. The refrigerant tank 74 and the water tank 77 are also called inner tanks 74 and 77. Each of the water tanks 73 and 77 is connected so as to communicate with both ends of the water tube 43a. Each of the refrigerant tanks 74 and 76 is connected to communicate with both ends of the refrigerant tube 16a. The refrigerant | coolant heat exchanger 16 as a refrigeration cycle evaporator is comprised by the some refrigerant | coolant tube 16a. The plurality of water tubes 43a constitute a radiator 43 as a heat source radiator.

The refrigerant tube 16a is a heat exchange tube through which the refrigerant RF flows. The refrigerant tube 16a is a flat tube having a flat cross-sectional shape perpendicular to the longitudinal direction.

The water tube 43a is a heat exchange tube through which a medium for adjusting the temperature of the heat source HS flows. The water tube 43a is a flat tube having a flat cross-sectional shape perpendicular to the longitudinal direction. Hereinafter, the refrigerant tube 16a and the water tube 43a are referred to as tubes 16a and 43a.

The plurality of tubes 16a and 43a are arranged such that the wide flat surfaces of the outer surfaces thereof are substantially parallel to the flow of the air UR. The plurality of tubes 16a and 43a are arranged at a predetermined interval from each other. Air passages 16b and 43b through which the air UR flows are formed around the plurality of tubes 16a and 43a. The air passages 16b and 43b are used as heat dissipation air passages.

Fins 50 are disposed in the air passages 16b and 43b. The fin 50 is an outer fin for promoting heat exchange between the tubes 16a and 43a and the air UR. The fin 50 is joined to the two tubes 16a and 43a adjacent in the row. Furthermore, the fin 50 is joined to the two tubes 16a and 43a located in the flow direction of the air UR. Therefore, at least four tubes 16 a and 43 a are joined to one fin 50. The fin 50 integrates the refrigerant heat exchanger 16 and the radiator 43. The fin 50 is made of a thin metal plate having excellent heat conductivity. The fin 50 is a corrugated fin obtained by bending a thin plate into a wave shape. The fin 50 promotes heat exchange between the refrigerant RF and the air UR. The fin 50 promotes heat exchange between the cooling water WT and the air UR. At least some of the fins 50 are joined to both the refrigerant tube 16a and the water tube 43a. Therefore, the fin 50 also functions to enable heat transfer between the refrigerant tube 16a and the water tube 43a. The refrigerant tube 16 a and the water tube 43 a can transfer heat via the fins 50. The plurality of tubes 16 a and 43 a are arranged to be thermally coupled to at least a part of the heat exchanger 70. The two fins 50 arranged on both sides of one refrigerant tube 16a are corrugated fins in which a plurality of peaks are joined to both surfaces of the refrigerant tube 16a.

A plurality of tubes 16a and 43a and a plurality of fins 50 are laminated and joined to form a core portion. The core portion 71 provides heat exchange between a plurality of, for example, three fluids including the refrigerant RF, the cooling water WT, and the air UR. The core part 71 is also called a heat exchange part.

The tank parts 72 and 75 are arranged at both ends of the core part 71. Each of the two tank parts 72, 75 has outer tanks 73, 76 located away from the core part 71 and inner tanks 74, 77 adjacent to the core part 71. The inner tanks 74 and 77 are disposed between the outer tanks 73 and 76 and the core portion 71. The outer tanks 73 and 76 and the inner tanks 74 and 77 extend so as to cover almost the entire end portion of the core portion 71 at the end portion of the core portion 71. Therefore, the outer tank 73 and the inner tank 74 are stacked on one end of the core portion 71. An outer tank 76 and an inner tank 77 are also stacked on the other end of the core portion 71.

In this embodiment, the outer tank 73 provides a distribution tank and a collecting tank for the cooling water WT. The distribution tank distributes the cooling water WT to the plurality of water tubes 43a. The collecting tank collects the cooling water WT from the plurality of water tubes 43a.

The outer tank 76 provides a distribution tank and a collection tank for the refrigerant RF. The distribution tank distributes the refrigerant RF to the plurality of refrigerant tubes 16a. The collecting tank collects the refrigerant RF from the plurality of refrigerant tubes 16a.

At one end of the core portion 71, an outer tank 73 for the cooling water WT and an inner tank 74 for the refrigerant RF are arranged. At the other end of the core portion 71, an outer tank 73 for the refrigerant RF and an inner tank 74 for the cooling water WT are arranged. That is, a tank for the refrigerant RF and a tank for the cooling water WT are arranged at both ends of the core portion 71.

The tank parts 72 and 75 enable the tubes 16a and 43a to be relatively freely arranged. For example, the tubes 16a or the tubes 43a are distributed and arranged in the upstream row 71c and the downstream row 71d along the flow direction of the air UR. In the illustrated example, the entire downstream row 71d is occupied by the refrigerant tube 16a. The upstream row 71c is occupied by the refrigerant tube 16a and the water tube 43a.

The tank of the refrigerant heat exchanger 16 and the tank of the radiator 43 can be formed at least partially by the same member. The refrigerant tube 16a, the water tube 43a, the tank, and the fin 50 are made of an aluminum alloy. These parts are brazed.

As shown in FIGS. 2 and 3, a first tank 16c for collecting or distributing refrigerant and cooling water is arranged at one end in the longitudinal direction of the tubes 16a and 43a, and below in the drawing. Yes. The first tank 16c is also referred to as a refrigerant tank because it accepts the refrigerant and discharges the refrigerant. The 1st tank 16c also provides the connection part which guides cooling water from one water tube 43a to the other water tube 43a.

The first tank 16c includes a connection plate member 161 connected to the refrigerant tube 16a and the water tube 43a arranged in two rows, an intermediate plate member 162 fixed to the connection plate member 161, and a first tank member 163. Have The connection plate member 161 is provided with a through-hole penetrating the front and back at portions corresponding to the plurality of tubes 16a and 43a. In these through holes, a plurality of tubes 16a, 16b are disposed and fixed.

The part corresponding to the refrigerant | coolant tube 16a of the intermediate | middle plate member 162 is provided with the through-hole 162a which penetrates the front and back. The refrigerant tube 16a is disposed through the through hole 162a. In the first tank 16c, the refrigerant tube 16a protrudes from the water tube 43a toward the first tank 16c. The first tank member 163 is fixed to the connection plate member 161 and the intermediate plate member 162, thereby forming therein a collection chamber 163a for collecting refrigerant and a distribution chamber 163b for distributing refrigerant. The first tank member 163 is formed in a W shape when viewed from the longitudinal direction by pressing a flat metal. A central portion of the first tank member 163 is joined to the intermediate plate member 162. The collecting chamber 163a and the distribution chamber 163b are partitioned as independent chambers. The collecting chamber 163a is disposed on the upstream side of the air UR, and the distribution chamber 163b is disposed on the downstream side.

A plate-like lid member is fixed to both ends in the longitudinal direction of the first tank member 163. One end of the distribution chamber 163b is connected to an inlet pipe 164 through which the refrigerant flows. An outlet pipe 165 for allowing the refrigerant to flow out is connected to one end of the collecting chamber 163a.

A second tank 43c for collecting or distributing refrigerant and cooling water is disposed on the other end in the longitudinal direction of the plurality of tubes 16a and 43a, and in the upper part of the drawing. The second tank is also called a water tank because it is responsible for receiving cooling water and discharging cooling water. The second tank also provides a connecting portion for guiding the refrigerant from one refrigerant tube 16a to another refrigerant tube 16a.

The second tank 43c basically has the same configuration as the first tank 16c. The second tank 43 c includes a connection plate member 431, an intermediate plate member 432, and a second tank member 433. A portion of the intermediate plate member 432 corresponding to the water tube 43a is provided with a through hole 432a penetrating the front and back. A water tube 43a is disposed through and fixed to the through hole 432a. In the second tank 43c, the water tube 43a protrudes from the refrigerant tube 16a toward the second tank 43c. Further, the second tank member 433 forms an upstream chamber 433b positioned upstream in the flow direction of the air UR and a downstream chamber 433a positioned downstream of the chamber 433b in the flow direction of the air UR. Since the chamber 433a distributes the cooling water, it is also called a distribution chamber 433a. The chamber 433b is also referred to as a collecting chamber 433b because it collects cooling water.

A plate-like lid member is fixed to both ends of the second tank member 433 in the longitudinal direction. An inlet pipe 435 through which cooling water flows is connected to one end of the distribution chamber 433a. An outlet pipe 434 through which refrigerant flows out is connected to one end of the collecting chamber 433b.

The refrigerant RF flows into the distribution chamber 163b of the first tank 16c via the inlet pipe 164, and flows into the refrigerant tube 16a in the downstream row. The refrigerant flows from the bottom to the top in the drawing in the refrigerant tubes 16a in the downstream row. The refrigerant that has flowed out of the downstream-line refrigerant tube 16a flows into the upstream-line refrigerant tube 16a through the chamber of the second tank 43c. The refrigerant flows from the upper side to the lower side of the refrigerant tube 16a in the upstream row. The refrigerant that has flowed out of the refrigerant tube 16a in the upstream row flows out from the outlet pipe 165 after collecting in the collecting chamber 163a of the first tank 16c. Therefore, in the heat exchanger 70, the refrigerant flows in a U-turn shape from the downstream row to the upstream row.

The cooling water WT flows into the distribution chamber 433a of the second tank 43c via the inlet pipe 435 and flows into the downstream water tube 43a. The cooling water flows from the top to the bottom in the figure in the downstream water tube 43a. The refrigerant that has flowed out of the downstream water tube 43a flows into the upstream water tube 43a through the chamber of the first tank 16c. The cooling water flows from the bottom to the top of the water tube 43a in the upstream row. The cooling water flowing out from the upstream water tube 43a collects in the collecting chamber 433b of the second tank 43c and then flows out from the outlet pipe 434. Therefore, in the heat exchanger 70, the cooling water flows in a U-turn shape from the downstream row to the upstream row.

FIG. 4 shows a cross section of the second tank 43 c, that is, the tank portion 72. The first tank 16c, that is, the tank portion 75 also has the same structure. The tank part 72 includes a first tank member 431 facing the core part 71 and a second tank member 433 facing the outside. Further, the tank unit 72 includes an intermediate plate member 432 provided between the first tank member 431 and the second tank member 433. These members 431, 432, and 433 are joined so as to partition the outer tank 73 and the inner tank 74 therebetween. In the illustrated example, the second tank member 433 is provided by a member having a W-shaped cross section. The second tank member 433 is located on the upstream side with respect to the flow direction of the air UR, the upstream ridge that provides the chamber 433b, and the downstream ridge that is located on the downstream side of the upstream ridge and provides the chamber 433a. And have. It can be said that the second tank member 433 forms an upstream chamber UPC and a downstream chamber DWC with respect to the flow direction of the air UR. As illustrated, the upstream chamber UPC and the downstream chamber DWC are partitioned. Therefore, the second tank member 433 partitions the upstream chamber UPC and the downstream chamber DWC extending in the row direction RD in the two protrusions.

The tank portions 72 and 75 and the plurality of tubes 16a and 43a are connected to flow the refrigerant RF and the cooling water WT. A part of the plurality of tubes 16 a and 43 a is connected to communicate with the inside of the outer tanks 73 and 76. The remaining portions of the plurality of tubes 16 a and 43 a are connected to communicate with the inside of the inner tanks 74 and 77. The partial tubes 16a and 43a pass through the walls of the inner tanks 74 and 77, that is, the first tank member 431, and further extend across the inner tanks 74 and 77. Has been inserted.

As shown in the figure, in the tank portion 72, the water tube 43 a is connected so as to communicate with the inside of the outer tank 73. The refrigerant tube 16 a is connected so as to communicate with the inside of the inner tank 74. The water tube 43 a passes through the wall of the inner tank 74, that is, the first tank member 431, extends further across the inner tank 74, and is inserted into the outer tank 73.

In FIG. 5, the solid line arrows indicate the flow of the refrigerant RF. Dashed arrows indicate the flow of the cooling water WT. The refrigerant RF supplied to the heat exchanger 70 flows through the refrigerant tubes 16a in the upstream row 71c after flowing through the refrigerant tubes 16a in the downstream row 71d. For this reason, it is possible to efficiently exchange heat with the air UR. In the refrigerant heat exchanger 16, the flow path cross-sectional area provided by the tanks 72 and 75 and the plurality of refrigerant tubes 16a increases continuously or stepwise from upstream to downstream of the flow of the refrigerant RF. Is set as follows.

The cooling water WT supplied to the heat exchanger 70 flows through the water tube 43a in the upstream row 71c after flowing through the water tube 43a in the downstream row 71d. For this reason, it is possible to efficiently exchange heat with the air UR. Moreover, when the cooling water WT is low temperature, the leeward side of the core part 71 tends to become low temperature. For this reason, generation | occurrence | production of frost can be correctly detected with the temperature sensor 23 arrange | positioned at the leeward side of the core part 71. FIG.

The refrigerant RF and the cooling water WT flow as counterflows in most parts of the heat exchanger 70. For this reason, efficient heat exchange can be provided also between refrigerant | coolant RF and the cooling water WT.

As shown in FIG. 6, the plurality of tubes 16a and 43a are arranged in a row in a direction orthogonal to the flow of the air UR. Furthermore, the plurality of tubes 16a and 43a are arranged in multiple rows along the flow direction of the air UR. The plurality of tubes 16a and 43a form a plurality of rows including at least the upstream row 71c and the downstream row 71d with respect to the flow direction of the air UR. The plurality of tubes 16a and 43a can be arranged in two rows. The plurality of tubes 16a and 43a are arranged so as to form an upstream row 71c located on the upstream side in the flow direction of the air UR and a downstream row 71d located on the downstream side of the upstream row 71c.

The refrigerant tubes 16a and the water tubes 43a are alternately arranged in both the upstream row 71c and the downstream row 71d. Therefore, the air passage 16b for heat absorption and the air passage 43b for heat dissipation are shared. Fins 50 are disposed in the common passages 16b and 43b.

In the row, at least in part, the refrigerant tube 16a and the water tube 43a are adjacent to each other. In the row, at least in part, the water tubes 43a can be positioned on both sides of the refrigerant tube 16a. In the row, at least in part, the refrigerant tubes 16a can be positioned on both sides of the water tube 43a. In at least part of the rows, the refrigerant tubes 16a and the water tubes 43a can be alternately positioned. At least in the upstream row 71c, the refrigerant tubes 16a and the water tubes 43a are alternately arranged so that the water tubes 43a are positioned on both sides of the refrigerant tube 16a. That is, in the heat exchanger 70, the water tubes 43a are positioned on both sides of the refrigerant tube 16a on the inflow side of the air UR, and they are arranged side by side. According to this configuration, the refrigerant tubes 16a can be dispersed in a wide range.

The refrigerant tube 16a and the water tube 43a are arranged next to one refrigerant tube 16a so that one water tube 43a is located via the fin 50. In at least a part of the upstream row 71c of the heat exchanger 70, one refrigerant tube 16a is disposed between the two water tubes 43a. Further, in at least a part of the upstream row 71c of the heat exchanger 70, one water tube 43a is disposed between the two refrigerant tubes 16a. In other words, the refrigerant tubes 16a and the water tubes 43a are alternately arranged at least in the upstream row 71c. Furthermore, the refrigerant tubes 16a and the water tubes 43a can be alternately arranged also in the downstream row 71d.

As shown in the figure, in at least a part of the upstream row 71c, the refrigerant tubes 16a and the water tubes 43a are arranged in the row direction RD. Further, in at least a part of the upstream row 71c, the refrigerant tubes 16a and the water tubes 43a are arranged side by side in the row direction RD. In other words, the refrigerant tube 16a and the water tube 43a are positioned at the same position with respect to the flow direction of the air UR.

In this embodiment, the refrigerant tube 16a and the water tube 43a are arranged side by side in the column direction RD in at least a part of the downstream column 71d. This configuration is advantageous for detecting the influence from both the refrigerant tube 16a and the water tube 43a by the temperature sensor 23. For example, when the air UR is cooled by both the refrigerant tube 16a and the water tube 43a, the average temperature can be detected without being biased to either the low temperature of the refrigerant tube 16a or the low temperature of the water tube 43a. .

The heat exchanger 70 is arranged so that the wide side surfaces of the plurality of tubes 16a and 43a spread along the vertical direction of the gravity direction. When condensed water adheres to the heat exchanger 70, the condensed water is generated in a low temperature portion. In the heat exchanger 70, the refrigerant RF functions as a low temperature medium. Condensed water adheres to the surface of the refrigerant tube 16a at an early stage. A large amount of condensed water is generated on the surface of the refrigerant tube 16a. The condensed water flows and spreads on the refrigerant tube 16a. For this reason, a water film is formed on the surface of the refrigerant tube 16a. Condensed water flows along the water film from top to bottom and is discharged. The refrigerant tube 16 a provides a drainage path for the condensed water in the heat exchanger 70. On the other hand, the water tube 43a is relatively hot. For this reason, the condensed water which generate | occur | produces on the surface of the water tube 43a is few. Therefore, it is difficult to form a water film for flowing condensed water on the surface of the water tube 43a. In the heat exchanger 70, since the refrigerant | coolant tube 163a is arrange | positioned adjacent to all the air passages 16b and 43b, favorable drainage is provided. In this embodiment, the refrigerant tubes 16a are arranged in both the upstream row 71c and the downstream row 71d. Therefore, the drainage path for the condensed water is formed in both the upstream row 71c and the downstream row 71d, so that the drop of water droplets into the air UR flow is suppressed.

When the refrigerant circuit 10 is operated, the passenger compartment is cooled. The cooling operation is activated by a switch operated by a vehicle user. The refrigerant flows through the refrigerant circuit 10 as indicated by solid line arrows. The high-pressure refrigerant discharged from the compressor 11 flows into the outdoor heat exchanger 21. The high-pressure refrigerant that has flowed into the outdoor heat exchanger 21 radiates heat to the air AR blown by the fan 17. The refrigerant flowing out of the outdoor heat exchanger 21 is decompressed and expanded by the expansion valve 19. The refrigerant flowing out of the expansion valve 19 flows into the indoor heat exchanger 20, absorbs heat from the air UR, and evaporates. Thereby, the air UR is cooled. The refrigerant flowing out of the indoor heat exchanger 20 is sucked into the compressor 11 and compressed again.

The control device 100 operates the refrigerant circuit 10 in order to provide the cooling operation. When the refrigerant circuit 10 is operated, the refrigerant evaporates in the refrigerant heat exchanger 16. The air UR is cooled by the evaporative refrigerant. As a result, cooling in the passenger compartment is provided. At this time, the operation of the compressor 11 is controlled based on the temperature detected by the temperature sensor 23, and the generation of frost in the heat exchanger 70 is suppressed.

The control device 100 operates the cooling water circuit 40 so as to maintain the temperature of the heat source HS in a desired temperature range. When the cooling water circuit 40 is operated, the cooling water WT circulates in the cooling water circuit 40. In one aspect, the control device 100 controls the cooling water circuit 40 so as to maintain the temperature of the cooling water WT near the reference temperature. The cooling water WT exchanges heat with the air UR in the radiator 43. The radiator 43 functions as a cooler that cools the air UR or a heater that heats the air UR according to the temperature of the cooling water WT. The cooling water WT also exchanges heat with the refrigerant heat exchanger 16, that is, the refrigerant RF, in the radiator 43. The radiator 43 functions as a radiator that cools the cooling water WT with the refrigerant RF.

When the cooling water circuit 40 is operated, the cooling water WT exchanges heat with the air UR in the radiator 43. As a result, the temperature of the heat source HS is adjusted via the cooling water WT. In typical operating conditions, cooling of the heat source HS is provided. Thus, the control device 100 can be configured to control the cooling water circuit 40 so as to radiate heat from the cooling water WT to the air UR. According to this configuration, the cooling water WT can be cooled by heat radiation from the cooling water WT to the air UR. Since the cooled cooling water WT is supplied to the heat source HS, the heat source HS can be cooled using the air UR.

The control device 100 can be configured to cool the heat source HS without considering air conditioning when there is no user in the vehicle. For example, when charging the battery during parking, the temperature of the battery as the heat source HS can be adjusted using the blower 32.

The control device 100 can operate the cooling water circuit 40 so as to use the temperature of the cooling water WT for adjusting the temperature of the air UR. In this case, the radiator 43 functions as a cooler that cools the air UR or a heater that heats the air UR in accordance with the temperature of the cooling water WT.

The control device 100 can be configured to control the cooling water circuit 40 so as to cool the air UR with the cooling water WT. According to this configuration, the air UR can be cooled by the cooling water WT. As a result, the air UR can be cooled without depending on the refrigerant circuit 10 alone.

The control device 100 can adjust the rotation speed of the pump 41 based on the temperature detected by the temperature sensor 23. For example, when the temperature of the heat exchanger 70 becomes low enough to cause frost, the control device 100 increases the amount of heat released from the heat source HS to the radiator 43 by increasing the number of rotations of the pump 41, and the frost adheres. , Growth can be suppressed. For example, when the temperature of the heat exchanger 70 becomes excessively high, the control device 100 can suppress the amount of heat released from the heat source HS to the radiator 43 by reducing the rotation speed of the pump 41.

In this case, the air conditioner 1 includes a temperature sensor 23 that detects the temperature in the use-side heat exchanger 16. The control device 100 controls the refrigerant circuit 10 in the cooling application based on the temperature detected by the temperature sensor 23 and controls the cooling water circuit 40 based on the temperature detected by the temperature sensor 23. According to this configuration, the temperature sensor for controlling the refrigerant circuit 10 can be used for controlling the cooling water circuit 40. When the air temperature Te downstream of the heat exchanger 70 is detected by the temperature sensor 23, the flow rate of the cooling water circuit 40 is feedback controlled so that the air temperature Te matches the target temperature.

The control device 100 can operate both the refrigerant circuit 10 and the cooling water circuit 40. In this case, the air UR can be heated or cooled by the radiator 34 while the air UR is cooled by the refrigerant evaporated in the refrigerant heat exchanger 16. Furthermore, the coolant WT of the radiator 43 can be cooled by the refrigerant evaporated in the refrigerant heat exchanger 16. As a result, the heat source HS can be cooled by the refrigerant circuit 10 and the cooling water circuit 40.

The control device 100 can stop the supply of the cooling water WT to the radiator 43 by the cooling water circuit 40 and operate only the refrigerant circuit 10. In this case, the maximum cooling performance is exhibited.

The control device 100 can be configured to control the refrigerant circuit 10 and the cooling water circuit 40 so as to adjust the temperature of the cooling water WT by the refrigerant RF. According to this configuration, the temperature of the cooling water WT is adjusted by heat exchange between the refrigerant RF and the cooling water WT. For example, when the temperature of the refrigerant RF is lower than the temperature of the cooling water WT, the cooling water WT can be cooled by the refrigerant RF. Further, when the temperature of the refrigerant RF is higher than the temperature of the cooling water WT, the cooling water WT can be heated by the refrigerant RF. In this case, air conditioning by adjusting the temperature of the air UR and temperature control of the heat source HS by adjusting the temperature of the cooling water WT can be performed simultaneously.

The control device 100 can operate the cooling water circuit 40 during and / or after the operation of the refrigerant circuit 10 in order to remove frost from the heat exchanger 70 and / or frost. In this case, the heat exchanger 70 is heated by the radiator 34. As a result, frost adhesion and growth on the heat exchanger 70 can be suppressed.

The control device 100 can reduce the flow rate of the air UR or stop the flow of the air UR in order to promote heat exchange between the refrigerant RF and the cooling water WT in the heat exchanger 70. In this case, heat exchange between the refrigerant RF and the air UR and heat exchange between the cooling water WT and the air UR are suppressed, and heat exchange between the refrigerant RF and the air UR can be increased. The control device 100 can include a control unit that suppresses the flow rate of the air UR from the flow rate required for air conditioning in order to promote cooling of the heat source HS.

The air conditioner 1 can include an air volume adjusting device that adjusts the flow rate of the air UR in order to adjust the amount of heat exchange between the refrigerant RF and the cooling water WT. The wind regulation device can be provided by the blower 32 and the control device 100. According to this configuration, the amount of heat exchange between the refrigerant RF and the cooling water WT can be adjusted by the flow rate of the air UR. By reducing the flow rate of the air UR, it is possible to increase the cooling amount of the cooling water WT by the refrigerant RF or increase the heating amount of the cooling water WT by the refrigerant RF.

When the cooling water circuit 60 is operated, the cooling water circulates in the cooling water circuit 60. The heater core 12 heats the air UR with the hot water supplied from the cooling water circuit 60 to the heater core 12. Thereby, heating of a vehicle interior is possible.

The control device 100 can be configured to control the flow rate of the refrigerant RF or the flow rate of the cooling water WT in response to the adhesion of frost in the heat exchanger 70. According to this configuration, the flow rate of the refrigerant RF or the cooling water WT is adjusted in response to the adhesion of frost in the heat exchanger 70. For example, when the refrigerant RF cools the air UR, the control device 100 decreases the refrigerant flow rate in response to the attachment of frost. When cooling water WT is cooling air UR, control device 100 reduces the flow rate of cooling water WT. When the refrigerant RF cools the air UR and the cooling water WT heats the air UR, the control device 100 increases the flow rate of the cooling water WT. When the refrigerant RF heats the air UR and the cooling water WT cools the air UR, the control device 100 increases the flow rate of the refrigerant RF.

(Second Embodiment)
In the following description, changes and differences from the preceding embodiment will be mainly described. Subsequent embodiments are modifications based on any of the preceding embodiments. In the heat exchanger 70 of the above embodiment, the refrigerant tubes 16a and the water tubes 43a are alternately arranged in both the upstream row 71c and the downstream row 71d. Instead, the refrigerant tubes 16a and the water tubes 43a may be alternately arranged only in the upstream row 71c.

In this embodiment, the plurality of tubes 16a and 43a and the tank portions 72 and 73 provide a flow path between the refrigerant RF and the cooling water WT as illustrated in FIGS.

7, a chamber 433b upstream of the outer tank 73 provides an inlet and an outlet for the cooling water WT. A partition 73 a is provided in the upstream chamber 433 b of the outer tank 73. The partition 73a divides the heat exchanger 70 left and right, that is, in the column direction RD. The chamber 163a upstream of the outer tank 77 provides a communication part for allowing the cooling water WT to flow in a U-shape. As a result, the flow path of the cooling water WT is U-shaped when the core portion 71 is viewed from the front.

The chamber 163b downstream of the outer tank 76 provides an inlet and an outlet for the refrigerant RF. A partition 76 a is provided in the downstream chamber 163 b of the outer tank 76. The partition 76a divides the heat exchanger 70 left and right, that is, in the column direction RD. The chamber 433a downstream of the outer tank 73 provides a communication part for flowing the refrigerant RF in a U shape. As a result, the flow path of the refrigerant RF is U-shaped when the core portion 71 is viewed from the front.

The inner tank 74 communicates with a chamber 433a downstream of the outer tank 73. The inner tank 77 communicates with a chamber 163b downstream of the outer tank 76. The inner tanks 74 and 77 communicate with each other at both ends of the two refrigerant tubes 16a arranged in the flow direction of the air UR. Therefore, the inner tanks 74 and 77 are connected in parallel with the two refrigerant tubes 16a arranged in the row direction CD.

In FIG. 8, in the upstream row 71c, the refrigerant tubes 16a and the water tubes 43a are alternately arranged. In the downstream row 71d, only the refrigerant tube 16a is disposed. In this configuration, the number of refrigerant tubes 16a is greater than the number of water tubes 43a. For this reason, the total heat transfer area RFS of the refrigerant RF is set to be larger than the total heat transfer area WTS of the cooling water WT, that is, RFS> WTS. This configuration preferentially provides performance as a use side heat exchanger for cold pressure refrigerant.

The number of refrigerant tubes 16a in the downstream row 71d is larger than the number of water tubes 43a in the downstream row 71d. The number of water tubes 43a in the downstream row 71d is zero. The refrigerant tubes 16a are majority in the downstream row 71d. Therefore, the generation of condensed water can be biased toward the downstream row 71d. Many paths for condensed water are formed early in the downstream row 71d. By forming the drainage path in the downstream row 71d, the splash of water droplets into the flow of the air UR is suppressed.

Returning to FIG. 7, the refrigerant RF flows into the plurality of refrigerant tubes 16 a in the right half of the core portion 71 in the drawing via the downstream chamber 163 b and the inner tank 77. At this time, in one row, the refrigerant is supplied to the two refrigerant tubes 16a. Further, in the row adjacent to the row, the refrigerant is supplied to one refrigerant tube 16a located in the downstream column 71d. The refrigerant RF flows through the left half of the core 71 and then flows out of the heat exchanger 70.

The cooling water WT flows from the upstream chamber 433b into the plurality of water tubes 43a in the right half of the core portion 71 in the drawing. The cooling water WT flows through the left half of the core 71 after flowing through the right half of the core 71 and exits from the heat exchanger 70.

According to this configuration, more refrigerant tubes 16a are arranged in the downstream row 71d than in the upstream row 71c. For this reason, it is suitable for cooling the air UR. Further, more water tubes 43a are arranged in the upstream row 71c than in the downstream row 71d. For this reason, an excessive temperature drop at the upstream end of the core portion 71 can be suppressed. As a result, adhesion of frost to the core portion 71 can be suppressed.

In this embodiment, as shown in FIG. 8, the refrigerant tubes 16a and the water tubes 43a are arranged in the upstream row 71c, and only the refrigerant tubes 16a are arranged in the downstream row 71d. Instead, only the refrigerant tubes 16a may be arranged in the upstream row 71c, and the refrigerant tubes 16a and the water tubes 43a may be arranged in the downstream row 71d.

(Third embodiment)
In the heat exchanger 70 of the above embodiment, the refrigerant RF flow direction and the cooling water WT flow direction are opposite in the adjacent refrigerant tube 16a and water tube 43a. Instead, in this embodiment, as shown in FIG. 9, the flow directions of the refrigerant RF and the cooling water WT are the same. The cooling water WT flows from the upstream chamber 433b into the plurality of water tubes 43a in the left half of the core portion 71 in the drawing. The cooling water WT flows through the left half of the core portion 71, then flows through the right half, and exits from the heat exchanger 70.

According to this configuration, heat exchange between the refrigerant RF and the cooling water WT is suppressed. As a result, heat exchange between the refrigerant RF and the air UR and heat exchange between the cooling water WT and the air UR are promoted.

(Fourth embodiment)
In the heat exchanger 70 of the above embodiment, the refrigerant tubes 16a and the water tubes 43a are alternately arranged in the upstream row 71c. Instead, in this embodiment, as illustrated in FIG. 10, a refrigerant tube group including a plurality of refrigerant tubes 16 a and a water tube group including a plurality of water tubes 43 a are alternately arranged. In the illustrated example, a refrigerant tube group composed of two refrigerant tubes 16a and a water tube group composed of three water tubes 43a are alternately arranged. Also in this configuration, in at least a part of the core portion 71, the refrigerant tube 16a and the water tube 43a are arranged in the column direction RD. According to this configuration, a temperature distribution can be given in the upstream row 71c.

Instead of the illustrated example, one refrigerant tube 16a and a group of water tubes may be alternately arranged. Moreover, you may arrange | position the one water tube 43a and a refrigerant | coolant tube group alternately. Further, the number of refrigerant tubes 16a belonging to the refrigerant tube group and the number of water tubes 43a belonging to the water tube group may be varied. Also, any of the configurations exemplified above can be adopted in the downstream row 71d. Furthermore, the same arrangement structure as that of the upstream row 71c may be adopted for the downstream row 71d.

(Fifth embodiment)
In the said embodiment, both the refrigerant | coolant tube 16a and the water tube 43a were arrange | positioned only to the upstream line 71c. Instead, in this embodiment, as shown in FIG. 11, both the refrigerant tube 16a and the water tube 43a are arranged in both the upstream row 71c and the downstream row 71d.

The refrigerant tube 16a and the water tube 43a are disposed adjacent to the upstream row 71c. Furthermore, the refrigerant tube 16a and the water tube 43a are also arranged adjacent to the downstream row 71d. Furthermore, the refrigerant | coolant tube 16a and the water tube 43a are arrange | positioned along with the flow direction of the air UR, ie, along the row direction CD.

According to this configuration, since the refrigerant tubes 16a and the water tubes 43a are arranged in the downstream row 71d, the influence of the temperature of the refrigerant tubes 16a and the influence of the temperature of the water tubes 43a appear downstream of the heat exchanger 70. . For example, the temperature sensor 23 can detect the influence from both the refrigerant RF and the cooling water WT.

(Sixth embodiment)
In the above embodiment, the plurality of tubes 16a and 43a are arranged so as to form a plurality of rows. Instead, in this embodiment, as shown in FIG. 12, the refrigerant tube 16a and the water tube 43a are arranged to form a single row. Also in this configuration, the refrigerant tube 16a and the water tube 43a are disposed adjacent to each other in the column direction RD. In addition, the fins 50 are disposed between the refrigerant tube 16a and the water tube 43a.

(Seventh embodiment)
Instead of the above embodiment, as shown in FIG. 13, a refrigerant tube 16a and a water tube 43a may be arranged. In this configuration, two refrigerant tubes 16a and one water tube 43a are alternately arranged.

(Eighth embodiment)
In the above embodiment, the heat exchanger 70 that exchanges heat between the refrigerant RF, the cooling water WT, and the air UR is used only for the indoor heat exchanger 20. In addition, a similar heat exchanger 70 (270) can be adopted for the outdoor heat exchanger 21. In the following description, the outdoor heat exchanger 21 having the same components as the heat exchanger 70 described above is referred to as a heat exchanger 270.

14, the air conditioner 1 includes a heat pump cycle 2 to which the disclosed invention is applied. The heat pump cycle 2 includes a heat exchanger 270 to which the disclosed invention is applied. The heat pump cycle 2 includes a refrigerant circuit 10 and a cooling water circuit 40. This embodiment provides a heat pump cycle 2 that can effectively use waste heat from a power source to suppress frost and / or defrost the outdoor heat exchanger 21.

The air conditioner 1 is a device that uses heat pumped from the air by the heat pump cycle 2. The indoor heat exchanger 20 is also referred to as an indoor evaporator 20. The indoor evaporator 20 is the heat exchanger 70 described above. In this embodiment, the heater core 12 is provided by an indoor condenser. In this embodiment, the heater core 12 is referred to as an indoor condenser 12. The indoor condenser 12 is a heating heat exchanger that exchanges heat between the high-temperature and high-pressure refrigerant flowing through the indoor condenser 12 and the air UR after passing through the indoor evaporator 20.

The refrigerant circuit 10 is provided by a vapor compression refrigeration cycle capable of reversible operation. The refrigerant circuit 10 serves as both a heating refrigerant cycle of the air conditioner 1 and a cooling refrigeration cycle. The refrigerant circuit 10 provides a narrowly defined heat pump cycle that uses the air AR outside the passenger compartment as a heat source. The refrigerant circuit 10 causes the refrigerant RF to flow through a refrigerant tube 16a described later, and supplies the heat absorbed by the refrigerant RF to the use side heat exchanger 12. The refrigerant RF flowing through the refrigerant circuit 10 is a main medium for drawing up heat from the heat source. The refrigerant circuit 10 is also called a main medium circuit 10.

In the following description, suppressing frost adhesion in the outdoor heat exchanger 21 of the refrigerant circuit 10, that is, the heat source side heat exchanger, and suppressing the growth of the attached frost are referred to as frost suppression. Moreover, melting and removing frost adhering to the outdoor heat exchanger 21 is called defrosting. Moreover, the performance which opposes the fall of the heat exchange performance resulting from frost is called anti-frosting performance. Thus, anti-frosting performance is provided by frost suppression and / or defrosting.

The refrigerant circuit 10 heats or cools the air UR blown into the passenger compartment. The refrigerant circuit 10 can perform a heating operation for heating the air UR by heating the air UR and a cooling operation for cooling the air UR by cooling the air UR by switching the flow path. The refrigerant circuit 10 can perform a defrosting operation that melts and removes frost attached to the outdoor heat exchanger 21 during the heating operation. Furthermore, the refrigerant circuit 10 can execute a waste heat recovery operation in which the heat of the heat source HS is absorbed by the refrigerant during the heating operation. The plurality of operation modes are switched by the control device 100.

An indoor condenser 12 is provided on the discharge side of the compressor 11. The indoor condenser 12 provides a use side heat exchanger to which high-pressure refrigerant is supplied and heat is supplied from the high-pressure refrigerant. An expansion valve 213 for heating is provided downstream of the indoor condenser 12. The expansion valve 213 decompresses and expands the refrigerant that has flowed out of the indoor condenser 12 during the heating operation. The expansion valve 213 is a decompression unit for heating operation. The expansion valve 213 provides a decompressor that decompresses the high-pressure refrigerant and supplies the low-pressure refrigerant. The expansion valve 213 is driven to a fully opened state when the refrigerant circuit 10 is cooled. An outdoor heat exchanger 21 is provided downstream of the expansion valve 213.

The outdoor heat exchanger 21 functions as an evaporator that evaporates low-pressure refrigerant and exerts an endothermic effect during heating operation. The outdoor heat exchanger 21 provides an endothermic heat exchanger that exchanges heat between the air AR and the low-pressure refrigerant so that the low-pressure refrigerant absorbs heat. The outdoor heat exchanger 21 functions as a heat radiator that radiates high-pressure refrigerant during cooling operation. The outdoor heat exchanger 21 is provided by a heat exchanger 270 configured as a heat exchanger unit that can be handled as an integral unit.

The heat exchanger 270 includes a refrigerant heat exchanger 216 and a radiator 243. The refrigerant heat exchanger 216 is provided by the outdoor heat exchanger 21. The radiator 243 is also referred to as a second radiator 243. In this case, the radiator 43 of the heat exchanger 70 is called the first radiator 43.

It is desirable that the heat exchanger 270 has the configuration illustrated in FIG. In these configurations, the refrigerant tubes 16a occupy the majority in the downstream row 71d of the heat exchanger 270. Therefore, in the heat exchanger 270, the radiator 243 provided by the water tube 43a is disposed upstream of the outdoor refrigerant heat exchanger 216 provided by the refrigerant tube 16a. According to this configuration, the heat acquired by the cooling water WT in the use side heat exchanger 16 can be given to the low-pressure refrigerant of the outdoor refrigerant heat exchanger 216 in the heat exchanger 270.

In the heat exchanger 270, it is desirable that the refrigerant tube 16a and the water tube 43a are thermally coupled by fins. Moreover, it is desirable that the refrigerant tube 16a and the water tube 43a are disposed adjacent to each other in at least a part of the upstream row or the downstream row. According to this configuration, the heat acquired by the cooling water WT in the usage-side heat exchanger 16 can be given to the low-pressure refrigerant of the outdoor refrigerant heat exchanger 216 via the fins in the heat exchanger 270.

The cooling water WT flows through the radiator 243. The radiator 243 exchanges heat between the cooling water WT of the cooling water circuit 40 and the air AR. Further, the radiator 243 supplies the heat of the cooling water WT to the outdoor heat exchanger 21 and the heat exchanger 270 including the outdoor heat exchanger 21. The radiator 243 holds an auxiliary medium that stores heat and supplies the stored heat to the endothermic heat exchanger, that is, the cooling water WT. The radiator 243 provides an auxiliary heat exchanger disposed adjacent to the outdoor heat exchanger 21.

An electric three-way valve 15b is connected downstream of the outdoor heat exchanger 21. The three-way valve 15b is controlled by the control device 100. The three-way valve 15b constitutes a refrigerant channel switching means. The three-way valve 15b directly connects the outlet of the outdoor heat exchanger 21 and the inlet of the accumulator 18 without a heat exchanger during heating operation. The three-way valve 15b connects the outlet of the outdoor heat exchanger 21 and the inlet of the cooling expansion valve 19 during cooling operation. The control device 100 provides control means for controlling the amount of refrigerant flowing in the refrigerant circuit 10 and the flow path. The amount of refrigerant is controlled by adjusting the refrigerant discharge capacity of the compressor 11. The flow path of the refrigerant is switched and controlled by controlling the expansion valve 213 and the three-way valve 15b. As a result, the heat pump cycle 2 includes cycle switching devices 213 and 15b that switch the flow path between a heating application and a cooling application. The cycle switching devices 213 and 15b control the flow paths so that the outdoor refrigerant heat exchanger 216 functions as an endothermic heat exchanger during heating, and the outdoor refrigerant heat exchanger 216 functions as a radiant heat exchanger during cooling. Heating is a heating application for heating an object. Cooling is a cooling application for cooling an object. The refrigerant circuit 10 can be switched between a heating application and a cooling application.

Further, the control device 100 provides a control means for controlling the flow and flow path of the cooling water in the cooling water circuit. The cooling water is controlled by controlling the pump 41 and the flow rate adjusting valve 45.

An indoor evaporator 20 is provided downstream of the expansion valve 19. An accumulator 18 is provided downstream of the indoor evaporator 20. The flow path that is formed by the three-way valve 15b during the heating operation and directly communicates with the accumulator 18 from the three-way valve 15b constitutes a passage 20a that allows the refrigerant downstream of the outdoor heat exchanger 21 to flow around the indoor evaporator 20. ing. The accumulator 18 is a gas-liquid separator for low-pressure refrigerant that separates the gas-liquid of the refrigerant that has flowed into the accumulator 18 and stores excess refrigerant in the cycle. A compressor 11 is provided downstream of the gas-phase refrigerant outlet of the accumulator 18. The accumulator 18 functions to prevent liquid compression of the compressor 11 by suppressing the suction of the liquid phase refrigerant into the compressor 11.

The cooling water circuit 40 may supply heat to the refrigerant circuit 10. The cooling water WT flowing in the cooling water circuit 40 is an auxiliary medium for assisting the pumping of heat by the main medium circuit 10. The cooling water circuit 40 is also referred to as an auxiliary medium circuit 40.

The cooling water circuit 40 is also a heat source that supplies heat for suppressing frost. The cooling water circuit 40 is also called a frost suppression medium circuit 40 for flowing a medium for suppressing frost. The cooling water circuit 40 flows cooling water WT for suppressing frost to a water tube 43a described later. The cooling water circuit 40 is also a heat source that supplies heat to the heat exchanger 70 for defrosting. The cooling water circuit 40 is also referred to as a defrosting medium circuit 40 for flowing a medium for defrosting. The cooling water circuit 40 flows the cooling water WT for defrosting to the water tube 43a. The cooling water circuit 40 maintains the temperature of the cooling water WT and the temperature of the heat source HS at a temperature higher than the temperature at which the refrigerant in the refrigerant tube 16a absorbs heat.

The cooling water circuit 40 includes components such as a bypass passage 44 for bypassing the radiator 43 and flowing cooling water, and an electric flow rate adjustment 45. The bypass passage 44 provides a flow path that bypasses the radiator 43. The cooling water circuit 40 provides a first flow path that passes through the heat source HS and the radiator 43 and a second flow path that passes through the heat source HS and the bypass passage 44. The flow rate adjustment valve 45 adjusts the flow rate through the bypass passage 44. The bypass passage 44 and the flow rate adjustment valve 45 provide a flow rate regulator that adjusts the flow rate of the cooling water WT supplied to the radiator 43. The flow rate adjuster includes a bypass passage 44 that bypasses the radiator 43 and flows the cooling water WT, and a valve device 45 that reduces the flow rate flowing through the radiator 43 by flowing the cooling water WT through the bypass passage 44.

The heat exchanger 270 provides heat exchange between the refrigerant RF, the cooling water WT, and the air AR. The heat exchanger 270 provides heat exchange between the refrigerant RF and the cooling water WT, between the refrigerant RF and the air AR, and between the cooling water WT and the air AR. The heat exchanger 270 has the same components as the heat exchanger 70 described above.

The air conditioner 1 of this embodiment includes a plurality of tubes 16a and 43a arranged in rows along a direction RD that intersects the flow direction CD of the unused air AR. 270. The plurality of tubes include a plurality of refrigerant tubes 16a and a plurality of water tubes 43a. The refrigerant tube 16a exchanges heat between the low-pressure refrigerant supplied from the refrigerant circuit 10 and the air AR. The water tube 43a exchanges heat between the cooling water WT supplied from the cooling water circuit 40 and the air AR. Furthermore, the water tubes 43a are arranged to be able to transfer heat with the refrigerant tubes 16a in at least a part of the rows. According to this configuration, a heat exchanger that exchanges heat between the refrigerant, the cooling water, and air is also used for the non-use side heat exchanger.

In this embodiment, the cooling water circuit 40 provides an auxiliary medium circuit 40. The cooling water WT is an auxiliary medium. The auxiliary medium circuit 40 includes an auxiliary medium heat exchanger 243 that cools the auxiliary medium. The auxiliary medium circuit 40 can cool the utilization air UR by supplying the auxiliary medium cooled by the auxiliary medium heat exchanger 243 to the auxiliary medium tube 43 a of the utilization side heat exchanger 70. The refrigerant circuit 10 includes an outdoor refrigerant heat exchanger 216 that exchanges heat between the unused air AR and the low-pressure refrigerant and absorbs heat by the low-pressure refrigerant. The auxiliary medium heat exchanger 243 cools the auxiliary medium with the low-pressure refrigerant or the unused air AR in the outdoor refrigerant heat exchanger 216. According to this configuration, the auxiliary medium can be cooled by the low temperature obtained by the refrigerant circuit 10 in the outdoor refrigerant heat exchanger 216 or the low temperature of the unused air AR.

The outdoor refrigerant heat exchanger 216 exchanges heat between the unused air AR and the low-pressure refrigerant in the heating application, and absorbs heat by the low-pressure refrigerant. The outdoor refrigerant heat exchanger 216 exchanges heat between the unused air AR and the high-pressure refrigerant in cooling applications, and dissipates heat from the high-pressure refrigerant. According to this configuration, the refrigerant circuit 10 can be used by switching between a heating application and a cooling application. The outdoor refrigerant heat exchanger 216 is used as a heat absorber in a heating application, and is used as a radiator in a cooling application. The control device 100 controls the air conditioner 1 so as to compensate for the performance degradation due to frost in the outdoor refrigerant heat exchanger 216. The control device 100 increases the flow rate or temperature of the auxiliary medium flowing through the auxiliary medium heat exchanger 243. The temperature of the auxiliary medium can be raised by increasing the heat load of the use side heat exchanger 70.

The control apparatus 100 can perform a cooling operation of the refrigerant circuit 10 so that the air UR is cooled by the refrigerant RF in the heat exchanger 70. At the same time, the control device 100 can operate the cooling water circuit 40 so as to adjust the temperature of the heat source HS. Further, the control device 100 can operate the cooling water circuit 40 so that the heat exchanger 70 is heated by the cooling water WT in the heat exchanger 70. For example, the cooling water WT defrosts the heat exchanger 70. In addition, the control device 100 can control the cooling water circuit 40 so that the heat exchanger 270 takes heat from the refrigerant RF to the cooling water WT. For example, the cool-down performance can be improved.

The control apparatus 100 can control the cooling water circuit 40 so that the air UR is cooled by the cooling water WT in the heat exchanger 70. In this configuration, the second radiator 243 exchanges heat with the air AR outside the vehicle. For this reason, the temperature of the cooling water WT may be comparable to the outside air temperature. In the above configuration, the low-temperature cooling water WT can be supplied to the first radiator 43. Therefore, when the temperature of the air UR is higher than the temperature of the cooling water WT, the air UR can be cooled and dehumidified by the cooling water WT.

The control device 100 can heat the refrigerant circuit 10 so that the air UR is heated by the indoor condenser 12. At the same time, the control device 100 can operate the cooling water circuit 40 so as to adjust the temperature of the heat source HS. Furthermore, the control device 100 can operate the cooling water circuit 40 so that the heat exchanger 270 is heated by the cooling water WT in the heat exchanger 270. For example, the cooling water WT defrosts the heat exchanger 270. Moreover, the control apparatus 100 can control the cooling water circuit 40 so that the air UR is heated by the cooling water WT in the heat exchanger 70. In this case, the waste heat of the heat source HS can be used for heating.

In this embodiment, the control device 100 performs the heating operation of the refrigerant circuit 10 so that the air UR is heated by the refrigerant RF in the indoor condenser 12, and cools the air UR by the cooling water WT in the heat exchanger 70. The cooling water circuit 40 can be operated.

When the refrigerant circuit 10 is heated, the low-temperature refrigerant RF is supplied to the heat exchanger 270. Therefore, the second radiator 243 can cool the cooling water WT below the temperature of the air AR. In this case, the low-temperature cooling water WT can be supplied to the first radiator 43. As a result, in the first radiator 43, the air UR can be cooled to a low temperature. Moreover, since the indoor condenser 12 can heat the air UR at this time, it can be heated while dehumidifying the air UR. Furthermore, since the cooling water WT heated in the first radiator 43 is supplied again to the first radiator 243, the heat taken from the air UR can be recovered in the refrigerant circuit 10 in the outdoor heat exchanger 21. Therefore, efficient dehumidifying heating can be executed.

In this case, the refrigerant circuit 10 is heated for heating. The cooling water WT cooled by the refrigerant RF or outside air in the heat exchanger 270, that is, the auxiliary medium, is supplied to the heat exchanger 70 to provide cooling, that is, a cooling action. In the heat exchanger 70, the cooling water WT, that is, the auxiliary medium functions as a low temperature medium. The low temperature medium is supplied to the radiator 43. At this time, condensed water is generated on the water tube 43a and grows. A large amount of condensed water is generated early on the surface of the water tube 43a through which the low-temperature medium flows. For this reason, the water tube 43 a provides a drainage path for condensed water in the heat exchanger 70.

(Ninth embodiment)
In the above embodiment, the heater core 12 is provided by the indoor condenser of the refrigerant circuit 10. Alternatively, as shown in FIG. 15, a refrigerant-water heat exchanger 24 that exchanges heat with the cooling water WT may be provided. In this configuration, the high-pressure refrigerant of the refrigerant circuit 10 is used as a heat source for the cooling water circuit 60.

(10th Embodiment)
In the said embodiment, the heat obtained by the heat pump cycle 2 was utilized for heating. Instead, as shown in FIG. 16, devices such as the battery BT may be warmed by the high-pressure refrigerant in the refrigerant circuit 10. In this configuration, the cooling water WT in the cooling water circuit 65 is heated by the refrigerant-water heat exchanger 24. The cooling water WT is circulated by the pump 66. Cooling water WT heats battery BT. For example, a large capacity battery such as a lithium ion battery mounted on an electric vehicle operates efficiently in a predetermined temperature range. According to this configuration, since the battery BT can be warmed, the temperature of the battery BT can be adjusted to a desired temperature range.

(Eleventh embodiment)
In the above embodiment, the indoor heat exchanger 20 is provided by the heat exchanger 70, and the outdoor heat exchanger 21 is provided by the heat exchanger 270. In addition, in this embodiment, the heater core 12 is also provided by a heat exchanger 370 similar to the heat exchanger 70. The heat exchanger 370 is a use side heat exchanger for high-pressure refrigerant for heating the air UR.

17, the heater core 12 is provided by a heat exchanger 370 having the same configuration as the heat exchanger 70. The heat exchanger 370 includes a refrigerant heat exchanger 316 that exchanges heat between the high-pressure refrigerant RF of the refrigerant circuit 10 and the air UR, and a third radiator 343 that exchanges heat between the cooling water WT and the air UR of the cooling water circuit 60. Is provided.

In this embodiment, the air conditioner 1 includes a plurality of tubes 16a and 43a arranged in rows along a direction RD that intersects the flow direction CD of the air UR. The plurality of tubes include a plurality of refrigerant tubes 16a and a plurality of water tubes 43a. The plurality of refrigerant tubes 16a exchange heat between the high-pressure refrigerant supplied from the refrigerant circuit 10 and the air UR. The plurality of water tubes 43a exchange heat between the cooling water WT supplied from the cooling water circuit 60 and the air UR. Furthermore, the water tubes 43a are arranged to be able to transfer heat with the refrigerant tubes 16a in at least a part of the rows.

That is, the refrigerant circuit 10 when performing the heating operation employs the heat exchangers 270 and 370 for both the use side heat exchanger 12 and the heat source side heat exchanger 21. In other words, the refrigerant circuit 10 in the heating operation employs heat exchangers 270 and 370 for both the high-pressure side heat exchanger 12 and the low-pressure side heat exchanger 21.

According to this configuration, the refrigerant circuit 10 supplies the high-pressure refrigerant to the refrigerant tube 16a of the use side heat exchanger 12. According to this configuration, heating of the air UR and heating of the cooling water WT can be provided by the high-pressure refrigerant. The heat exchanger 370 can heat the air UR by the refrigerant circuit 10. The heat exchanger 370 can heat the air UR with the cooling water WT of the cooling water circuit 60. Further, the coolant WT and the heat source HS of the coolant circuit 60 can be heated from the refrigerant circuit 10 via the heat exchanger 370. In some cases, the cooling water WT and the heat source HS of the cooling water circuit 60 can be heated by the air UR.

(Twelfth embodiment)
In the said embodiment, the cold heat obtained by the refrigerant circuit 10 was utilized for the air conditioning. Instead, the cold energy obtained by the refrigerant circuit 10 may be used for cooling purposes other than air conditioning.

FIG. 18 shows an embodiment in which a heat exchanger 470 having the same configuration as that of the heat exchanger 70 is applied to a cold storage cabinet 80 for a vehicle. The cold / hot warehouse 80 is mounted on a vehicle and has a small room for cooling or heating an article such as a beverage. The cold / hot warehouse 80 includes a heat exchanger 470, a blower 81, and a pressure reducing valve 82. The heat exchanger 470 includes a refrigerant heat exchanger 416 and a cooling water heat exchanger 443. The refrigerant heat exchanger 416 exchanges heat between the refrigerant supplied from the refrigerant circuit 10 and the air in the warehouse. The cooling water heat exchanger 443 exchanges heat between the cooling water WT supplied from the cooling water circuit 40 and the air in the warehouse. Furthermore, the refrigerant heat exchanger 416 and the cooling water heat exchanger 443 are thermally coupled to each other through members such as the fins 50 and air in the cabinet. Thus, the heat exchanger 470 also provides heat exchange between the refrigerant RF and the cooling water WT. The blower 81 blows air so that the air in the warehouse passes through the heat exchanger 470. The pressure reducing valve 82 is opened when the cold / hot warehouse 80 is used for cooling, and the pressure of the refrigerant RF is reduced and supplied to the refrigerant heat exchanger 416. The pressure reducing valve 82 is closed when the cold / hot warehouse 80 is not used for cooling purposes.

When the cold / hot warehouse 80 is used for cooling, the refrigerant heat exchanger 416 cools the air in the warehouse. When the cold / hot warehouse 80 is used for heating, the air in the warehouse is heated by the cooling water heat exchanger 443. Furthermore, when the heat source HS needs to be cooled, the coolant WT is cooled by the refrigerant heat exchanger 416, and the heat source HS is cooled.

In this configuration, the air used is the air in the cabinet that can store the articles. According to this structure, temperature control of the articles | goods in a store | warehouse | chamber and temperature control of the heat source HS can be provided. By using the heat exchanger 470, the cold heat obtained from the refrigerant circuit 10 is used for air cooling, the hot heat obtained from the heat source HS is used for air heating, and the cold heat source HS obtained from the refrigerant circuit 10 is used. Can be used for cooling.

(13th Embodiment)
FIG. 19 shows a part of the heat exchanger 70 according to this embodiment. The illustrated arrangement is applicable to the heat exchangers 70, 270, 470 described above. The plurality of tubes 16a and 43a are arranged so as to form a row in a direction orthogonal to the flow direction of the air UR. The plurality of tubes 16a and 43a are arranged so as to form an upstream row 71c located on the upstream side in the flow direction of the air UR and a downstream row 71d located on the downstream side of the upstream row 71c.

Only the refrigerant tubes 16a are arranged in the upstream row 71c. The refrigerant tube 16a and the water tube 43a are arranged in the downstream row 71d. In at least a part of the downstream row 71d, the refrigerant tube 16a and the water tube 43a are adjacent to each other. The refrigerant tubes 16a and the water tubes 43a are alternately arranged over the entire downstream row 71d. In this embodiment, the two water tubes 43a are not adjacent in the direction orthogonal to the flow direction of the air UR. In the upstream row 71c, the refrigerant tubes 16a are adjacent to all the air passages 16b and 43b. Also in the downstream row 71d, the refrigerant tubes 16a are adjacent to all the air passages 16b and 43b. Therefore, the refrigerant tubes 16a are adjacent to all the air passages 16b, 43b of all the rows 71c, 71d.

The adjacent water tubes 43 a in the upstream row 71 c are thermally coupled via the fins 50. The adjacent refrigerant tubes 16a and water tubes 43a in the downstream row 71d are thermally coupled via the fins 50. The fin 50 extends between the upstream row 71c and the downstream row 71d. The fin 50 is a corrugated fin formed in a corrugated plate shape. The fin 50 promotes heat exchange with the air UR. A plurality of louvers 50 a having slit-like openings are formed on the fin 50. The louver 50 a forms a plurality of slit-shaped openings on the fin 50. The louver 50 a forms a large number of fine gaps on the fin 50. The louver 50a promotes heat exchange with the air UR.

In the entire heat exchanger 70, the number of refrigerant tubes 16a is larger than the number of water tubes 43a. The refrigerant tube 16a is a majority in the upstream row 71c. The number of refrigerant tubes 16a in the upstream row 71c is larger than the number of water tubes 43a in the upstream row 71c. According to this configuration, generation of condensed water can be biased toward the upstream row 71c. In this embodiment, the number of water tubes 43a in the upstream row 71c is zero. The flow path cross-sectional area for the refrigerant RF provided by the plurality of refrigerant tubes 16a in the heat exchanger 70 is larger than the flow path cross-sectional area for the cooling water WT provided by the plurality of water tubes 43a in the heat exchanger 70. The cooling water WT is a high temperature medium. The refrigerant RF is a low temperature medium whose temperature is lower than that of the high temperature medium.

As shown in FIG. 20, the condensed water in the XX-XX section gradually changes after the heat exchanger 70 is operated as an evaporator. The first stage ST1, the second stage ST2, and the third stage ST3 in the figure correspond to the passage of time after the low-temperature medium starts flowing through the refrigerant tube 16a. As shown in the drawing, in the first stage ST1, water droplets DRP are generated on the surface of the refrigerant tube 16a and the surface of the fin 50. The number of water droplets DRP increases gradually, and the size of the water droplets DRP gradually increases.

Eventually, in the second stage ST2, the condensed water adhering to the surface of the refrigerant tube 16a flows in the direction of gravity. The condensed water forms a continuous water film FLM on the surface of the refrigerant tube 16a. At this time, since the condensed water flows, the thickness of the water film FLM is thin. On the fin 50, the water droplet DRP further grows. In the third stage ST3, water droplets on the fins 50 flow together with the film FLM on the refrigerant tube 16a. The water droplet DRP on the fin 50 contacts the film FLM before it grows large and flows away along the film FLM. While the cold medium is supplied to the refrigerant tube 16a, the state of the third stage ST3 is maintained. As a result, blockage of the air passage due to excessive growth of the water droplet DRP is avoided. Moreover, it is avoided that the water droplet DRP jumps out into the flow of the air UR.

As shown in FIG. 21, the condensed water in the XXI-XXI section gradually changes after the heat exchanger 70 is operated as an evaporator. As shown in the drawing, in the first stage ST1, water droplets DRP are generated on the surface of the refrigerant tube 16a and the surface of the fin 50. On the other hand, the low temperature medium is not supplied to the water tube 43a. For this reason, the water tube 43a does not become a low temperature which produces condensed water. For this reason, the water droplet DRP is not generated on the surface of the water tube 43a, or a very small amount is generated.

Eventually, in the second stage ST2, the condensed water adhering to the surface of the refrigerant tube 16a flows in the direction of gravity. The condensed water forms a continuous water film FLM on the surface of the refrigerant tube 16a. On the fin 50, the water droplet DRP further grows. At the same time, very few water droplets DRP may be generated on the surface of the water tube 43a.

In the third stage ST3, water droplets on the fins 50 flow together with the film FLM on the refrigerant tube 16a. The water droplet DRP on the fin 50 contacts the film FLM before it grows large and flows away along the film FLM. Very few water droplets DRP may remain on the surface of the water tube 43a. While the cold medium is supplied to the refrigerant tube 16a, the state of the third stage ST3 is maintained. As a result, blockage of the air passage due to excessive growth of the water droplet DRP is avoided. Moreover, it is avoided that the water droplet DRP jumps out into the flow of the air UR.

According to this embodiment, the water droplet DRP of the condensed water comes into contact with the film FLM formed on the surface of the refrigerant tube 16a and flows away before it grows to a size that closes the air passage. For this reason, jumping out of the water droplet DRP from the heat exchanger 70 can be suppressed.

22 shows the arrangement of the plurality of tubes 16a and 43a in the heat exchanger CMP of the comparative example. In the comparative example, one of the upstream row 71c and the downstream row 71d is provided by arranging only a plurality of water tubes 43a. The other of the upstream row 71c and the downstream row 71d is provided by arranging only a plurality of refrigerant tubes 16a. In the illustrated example, only the plurality of refrigerant tubes 16a are arranged in the upstream row 71c. Only a plurality of water tubes 43a are arranged in the downstream row 71d.

The condensed water in the section XX-XX in FIG. 22 changes as illustrated and described in FIG. FIG. 23 shows the transition of condensed water in the section XXIII-XXIII. In the heat exchanger CMP, the fins 50 are cooled by the refrigerant tubes 16a arranged in the upstream row 71c. In the downstream row 71d, the fin 50 has the lowest temperature. For this reason, in the first stage ST1, water droplets DRP are generated on the surface of the fin 50. The number of water droplets DRP increases gradually, and the size of the water droplets DRP gradually increases.

Eventually, in the second stage ST2, the water droplet DRP further grows on the fin 50. The water droplet DRP grows greatly without flowing along the vertical direction. In the third stage ST3, the water droplet DRP on the fin 50 reaches a size that closes the air passage on the fin 50. When the water droplet DRP becomes large, it is difficult for the water droplet DRP to flow even if it contacts the surface of the water tube 43a. This is because the surface of the water tube 43a is not continuously wet. As a result, the air passage is blocked by excessive growth of the water droplet DRP. In addition, the water droplet DRP is pushed by the flow of the air UR, and it becomes easy to jump out.

As described above, the heat exchanger CMP of the comparative example has a portion where the two water tubes 43a are adjacent to each other. In this part, the condensed water tends to grow large. For this reason, the air passages 16b and 43b may be blocked by the water droplet DRP, or the water droplet DRP may be scattered. On the other hand, in the heat exchanger 70 according to this embodiment, the refrigerant tubes 16a are adjacent to all the air passages 16b and 43b. For this reason, in all of the air passages 16b and 43b, a condensed water discharge path extending along the surface of the refrigerant tube 16a is provided.

(14th Embodiment)
FIG. 24 shows a control process S1 applicable to any of the preceding embodiments. The control process S2 includes cooling water control for adjusting the flow rate Gw of the cooling water for adjusting the temperature of the heat source HS. The control process S2 includes air conditioning control for adjusting the flow rate Gu of the air UR to be used.

In S11, the control device 100 determines whether or not the power for the air conditioner 1 is available. This process can be provided by determining whether the power switch or ignition switch of the vehicle is in the ON position or the OFF position. If power is not available, wait. When power becomes available, the process proceeds to S12.

In S12, the control device 100 determines whether or not the coolant temperature Tw exceeds a predetermined threshold temperature Tth. The threshold temperature Tth is a temperature indicating that the heat source HS is in an abnormally high temperature state when power is available. It is desirable that the cooling water temperature Tw accurately reflects the temperature of the heat source HS. For example, the temperature of the cooling water at the inlet to the heat source HS or the outlet of the heat source HS can be used. When the cooling water temperature Tw does not exceed the threshold temperature Tth (Tw <Tth or Tw = Tth), the process proceeds to S13. When the cooling water temperature Tw exceeds the threshold temperature Tth (Tw> Tth), the process proceeds to S15.

For example, if the vehicle has been parked under hot weather for a long time, the heat source HS may reach an excessively high temperature. In addition, when the flow of the cooling water WT is interrupted after operating the heat source HS under a large load, the heat source HS may reach an excessively high temperature. Utilizing the heat source HS under such excessively high temperature conditions is not desirable in order to maintain the performance of the heat source HS over a long period of time. For example, when the heat source HS is a battery, charging / discharging of the battery under an excessively high temperature condition is not desirable.

In S13, the control device 100 executes normal cooling water control. Here, the flow rate Gw of the cooling water WT passing through the heat source HS and the heat exchangers 43, 243, and 443 is controlled. For example, the flow rate Gw is adjusted based on a predetermined control characteristic as illustrated. In the illustrated example, the flow rate Gw is adjusted according to the cooling water temperature Tw. Thereby, the flow rate Gw is controlled so that the temperature of the heat source HS is maintained at a predetermined temperature.

In S14, the control device 100 starts normal air conditioning. Here, the normal air volume control is executed, and the air volume Gu of the air UR on the use side is adjusted. For example, the air volume Gu is adjusted based on a predetermined control characteristic as illustrated. In the illustrated example, the air volume Gu is adjusted according to the heat load Qac of the air conditioner 1. The air volume can be adjusted to increase as the heat load Qac for cooling or the heat load Qac for heating increases.

In S15, the control device 100 executes cooling water control adapted when the heat source HS is at an excessively high temperature. In S15, the flow rate Gw increased so as to be larger than the flow rate Gw given in S13 is given. As a result, the heat source HS is cooled by the increased flow rate Gw.

In S16, the control device 100 suspends the normal air conditioning control. Here, the air volume control adapted to the case where the heat source HS is at an excessively high temperature is executed. In S16, the air volume Gu suppressed to be smaller than the air volume Gu given in S14 is given. The air volume Gu is adjusted to be less than the control characteristic in S14. The air volume Gu may be adjusted to zero. As a result, air conditioning such as cooling is suspended.

According to this embodiment, the flow rate Gw and the air volume Gu are controlled so as to quickly eliminate the excessively high temperature of the heat source HS. If the heat source HS has an excessively high temperature immediately after the power becomes available, first, S15 and S16 are executed. Therefore, the flow rate Gw increased from the normal control characteristic is supplied. At the same time, the air volume Gu that is suppressed by the normal control characteristics is supplied.

Soon, when the cooling water temperature Tw does not exceed the threshold temperature Tth, S13 and S14 are executed. Therefore, when the heat source HS is cooled from an excessively high temperature state to a normal temperature range, the flow rate Gw decreases. At the same time, the air volume Gu increases.

S17 is performed in the embodiment including the heat exchanger 270. In S <b> 17, the control device 100 controls the air conditioner 1 to compensate for the deterioration in performance of the heating operation caused by frost attached to the outdoor refrigerant heat exchanger 216. The control device 100 increases the flow rate of the auxiliary medium flowing through the radiator 243, that is, the auxiliary medium heat exchanger 243 in accordance with the performance degradation due to frost in the outdoor refrigerant heat exchanger 216. Instead of or in addition to this, the control device 100 increases the amount of heat given to the auxiliary medium heat exchanger 243 by increasing the heat load of the use side heat exchanger 70. For example, the heat load can be increased by increasing the air volume Gu of the utilization air UR and / or the temperature of the introduced air. Due to the increase in heat load, the radiator 43 can apply heat to the cooling water WT. As a result, heat is applied to the auxiliary medium heat exchanger 243 via the cooling water circuit 40, and frost in the outdoor refrigerant heat exchanger 216 can be suppressed and removed.

The processing in S17 can be performed according to the performance reduction amount by detecting a performance reduction caused by frost adhering to the outdoor refrigerant heat exchanger 216. For example, it can be performed based on the temperature or pressure of the refrigerant in the outdoor refrigerant heat exchanger 216. Before and after the temperature or pressure reaches a predetermined threshold value, the flow rate of the cooling water WT can be increased or the temperature of the cooling water WT can be increased.

According to this embodiment, the control device 100 executes the temperature control of the heat generating device HS by the auxiliary medium circuit 40 in preference to the temperature control of the use air by the use side heat exchanger 70 after the power becomes available. . The flow rate Gw is decreased before and after the temperature related to the circuit 40 for the auxiliary medium, that is, the cooling water temperature Tw reaches a predetermined threshold temperature. The air volume Gu is increased before and after the temperature related to the circuit 40 for the auxiliary medium, that is, the cooling water temperature Tw reaches a predetermined threshold temperature.

According to this embodiment, when the heat source HS is in an excessively high temperature state, the air conditioning is substantially suspended and the temperature control of the heat source HS is prioritized. Thereafter, when the temperature of the heat source HS decreases, the suspension of the air conditioning is canceled and the air conditioning is substantially started. For this reason, the heat source HS can be protected. Further, by operating the refrigerant circuit 10 during the period in which the air conditioning is suspended, the high pressure and the low pressure necessary for the air conditioning can be generated. Thus, rapid air conditioning can be provided after the suspension of air conditioning is released.

(Fifteenth embodiment)
FIG. 25 shows a control process S2 applicable to any of the preceding embodiments. The control process S2 includes cooling water control for adjusting the flow rate Gw of the cooling water for adjusting the temperature of the heat source HS. The control process S2 includes air conditioning control for adjusting the flow rate Gu of the air UR to be used. The control process S2 is applied when the heat source HS includes a battery that can be charged by an external power source. The battery is charged from a generator mounted on the vehicle or an external power source. The external power source is, for example, a commercial power source or a small-scale power generation facility provided in a house or business office. For example, a battery as the heat source HS is charged via a cable connecting the vehicle and an external power source.

In S21, the control device 100 determines whether or not the battery is charged. This processing can be provided by determining whether the cable connects the vehicle and an external power source. The determination in S21 is also a process for determining whether or not the battery is rapidly charged. In rapid charging, since a high charging current flows through the battery, the temperature of the battery tends to increase. If not charging, the process proceeds to S13. If charging, proceed to S25.

In S13, the control device 100 executes the above-described normal cooling water control. In S14, the control device 100 starts the above-described normal air conditioning. When the battery is not being charged, the temperature of the battery is maintained at a desired temperature by normal cooling water control. The air conditioner 1 is controlled to provide a comfortable environment for the user.

In S25, the control device 100 executes the cooling water control adapted when the battery is being rapidly charged. In S25, the flow rate Gw increased so as to be larger than the flow rate Gw given in S13 is given. As a result, the heat source HS is cooled by the increased flow rate Gw.

The increase amount + Gw of the flow rate Gw can be set based on the state of charge SOC (State Of Charge) of the battery. The state of charge SOC indicates the amount of charge charged in the battery, that is, the remaining amount. The increase amount + Gw is set to a relatively large value when the state of charge SOC is low. The increase amount + Gw is set to a relatively small value when the state of charge SOC is high. As shown in the figure, the increase amount + Gw can be set to gradually decrease as the state of charge SOC increases. Further, the increase amount + Gw can be set so as to decrease stepwise at a predetermined threshold value SOC1. In these cases, the flow rate Gw is decreased before and after the charge amount reaches the predetermined value SOC1.

In S26, the control device 100 suspends normal air conditioning control. Here, the air volume control adapted to the case where the battery is being rapidly charged is executed. In S26, the air volume Gu suppressed to be smaller than the air volume Gu given in S14 is provided. The air volume Gu is adjusted to be less than the control characteristic in S14. The air volume Gu may be adjusted to zero. As a result, air conditioning such as cooling is suspended.

The air volume Gu can be suppressed by multiplying the control characteristic in S14 by the suppression coefficient Kur. The suppression coefficient is set between 0.0 and 1.0. The suppression coefficient Kur is set to a relatively small value when the state of charge SOC is low. The suppression coefficient Kur is set to a relatively large value when the state of charge SOC is high. As shown in the figure, the suppression coefficient Kur can be set to gradually increase as the state of charge SOC increases. Further, the suppression coefficient Kur can be set so as to increase stepwise at the predetermined threshold SOC2. In these cases, the air volume Gu is increased before and after the charge amount reaches the predetermined value SOC2.

According to this embodiment, the control device 100 executes the temperature control of the battery by the auxiliary medium circuit 40 in preference to the temperature control of the use air UR by the use side heat exchanger 70 when the battery is charged. When the battery is charged, the flow rate Gw and the air volume Gu are controlled so as to control the temperature of the battery to a desired temperature. When the battery is charged, first, S25 and S26 are executed. Therefore, the flow rate Gw increased from the normal control characteristic is supplied. At the same time, the air volume Gu that is suppressed by the normal control characteristics is supplied. As a result, if charging is started while the temperature control of the air used is being executed, the air volume Gu is reduced more than immediately before. The air volume Gu may be reduced to zero.

As soon as charging progresses, the state of charge SOC rises. The flow rate Gw is decreased before and after the state of charge SOC exceeds the threshold value SOC1. In addition, the air volume Gu is increased before and after the state of charge SOC exceeds the threshold value SOC2. When charging is completed, S13 and S14 are executed. Therefore, the flow rate Gw decreases when special temperature management for the battery is not required. At the same time, the air volume Gu increases.

According to this embodiment, when the battery is charged, the flow rate Gw is decreased before and after the amount of charge, that is, the state of charge SOC reaches the predetermined threshold value SOC1. When the battery is charged, the air volume Gu is increased before and after the amount of charge, that is, the state of charge SOC reaches a predetermined threshold value SOC2.

According to this embodiment, when the battery is charged with a large current, the air conditioning is substantially suspended and the temperature control of the battery is prioritized. Thereafter, when the charge amount of the battery increases, the suspension of the air conditioning is canceled and the air conditioning is substantially started. For this reason, the temperature control capability of the battery during charging, particularly the cooling capability, can be increased. Further, by operating the refrigerant circuit 10 during the period in which the air conditioning is suspended, the high pressure and the low pressure necessary for the air conditioning can be generated. Thus, rapid air conditioning can be provided after the suspension of air conditioning is released.

(Other embodiments)
Although the embodiments have been described above, the present disclosure is not limited to the above-described embodiments, and various modifications can be made without departing from the spirit of the present disclosure. The structure of the said embodiment is an illustration to the last, Comprising: The range of this indication is not limited to the range of these description. The scope of the present disclosure is indicated by the description of the scope of claims, and further includes meanings equivalent to the description of the scope of claims and all modifications within the scope.

For example, the means and functions provided by the control device can be provided by software only, hardware only, or a combination thereof. For example, the control device may be configured by an analog circuit.

In the above embodiment, cooling water is used as the auxiliary medium. Instead, a fluid that is excellent in heat transportability and can store heat, such as refrigerant, oil, gas, or the like, may be used.

In the above embodiment, the radiator 43 is provided in the cooling water circuit 40. In addition to this, a heat exchanger for radiating heat from the cooling water WT by heat exchange between the cooling water WT and the air AR may be provided. For example, a heat exchanger for heat radiation can be provided in parallel with the radiator 43 and the heat source HS.

In the above embodiment, the air passages 16 b and 43 b are provided in both the refrigerant heat exchanger 16 and the radiator 43. However, a configuration in which the air passage is not provided in the radiator 43 may be adopted. Moreover, the refrigerant | coolant tube 16a and the water tube 43a can be alternately arrange | positioned in all or one part of the heat exchanger 70. FIG. Moreover, the refrigerant | coolant tube 16a and the water tube 43a can be alternately arrange | positioned in all or one part of the upstream line of the heat exchanger 70. FIG. Moreover, the refrigerant | coolant tube 16a and the water tube 43a may be arrange | positioned so that 3 or more rows may be comprised regarding the flow direction of the air AR.

Claims (24)

1. A refrigerant circuit (10) including a compressor (11) for supplying high-pressure refrigerant by sucking and compressing low-pressure refrigerant, and a decompressor (19) for depressurizing the high-pressure refrigerant and supplying the low-pressure refrigerant;
   An auxiliary medium circuit (40, 60) configured separately from the refrigerant circuit, in which the auxiliary medium circulates;
   A plurality of refrigerant tubes (16a) for exchanging heat between the refrigerant supplied from the refrigerant circuit and the use air (UR), and the auxiliary medium and use air (UR) supplied from the auxiliary medium circuit. A use side heat exchanger (70, 370, 470) having a plurality of auxiliary medium tubes (43a) for heat exchange;
   A control device (100) for controlling the refrigerant circuit and the auxiliary medium circuit;
   The refrigerant tube (16a) and the auxiliary medium tube (43a) are:
   Arranged in a row along a direction (RD) intersecting the flow direction (CD) of the utilization air (UR);
   The heat utilization system in which the refrigerant tube (16a) and the auxiliary medium tube (43a) are arranged to be able to transfer heat in at least a part of the row.
2. The heat utilization system according to claim 1, wherein the auxiliary medium is a medium for adjusting the temperature of the heat generating device (HS, BT).
3. The utilization side heat exchanger includes fins (50) disposed in air passages (16b, 43b) formed between the refrigerant tube (16a) and the auxiliary medium tube (43a),
   The heat utilization system according to claim 1 or 2, wherein the refrigerant tube (16a) and the auxiliary medium tube (43a) can transfer heat via the fins.
4. The heat pump cycle according to any one of claims 1 to 3, wherein the number of the refrigerant tubes is larger than the number of the auxiliary medium tubes.
5. The refrigerant tube and the auxiliary medium tube are arranged to constitute at least an upstream row and a downstream row with respect to the flow direction of the utilization air,
   The heat pump cycle according to any one of claims 1 to 4, wherein the refrigerant tube is a majority in the upstream row.
6. The refrigerant tube and the auxiliary medium tube are arranged to constitute at least an upstream row and a downstream row with respect to the flow direction of the utilization air,
   The heat pump cycle according to any one of claims 1 to 4, wherein the refrigerant tube is a majority in the downstream row.
7. The heat utilization system according to any one of claims 1 to 6, wherein the control device controls the refrigerant circuit and the auxiliary medium circuit so as to adjust a temperature of the auxiliary medium by the refrigerant.
8. Furthermore, in order to adjust the heat exchange amount between the said refrigerant | coolant and the said auxiliary | assistant medium, the air volume adjusting device (32, 100) which adjusts the flow volume of the said utilization air is provided in any one of Claims 1-7. The described heat utilization system.
9. The heat utilization system according to any one of claims 1 to 8, wherein the control device controls the auxiliary medium circuit so as to cool the utilization air by the auxiliary medium.
10. The heat utilization system according to any one of claims 1 to 9, wherein the control device controls the auxiliary medium circuit so as to radiate heat from the auxiliary medium to the utilization air.
11. The heat utilization system according to any one of claims 1 to 10, wherein the control device controls the flow rate of the refrigerant or the flow rate of the auxiliary medium in response to frost adhesion in the use side heat exchanger. .
12. The heat utilization system according to any one of claims 1 to 11, wherein the refrigerant circuit supplies the low-pressure refrigerant to the refrigerant tube.
13. The auxiliary medium circuit (40) includes an auxiliary medium heat exchanger (243) for cooling the auxiliary medium,
    The heat utilization system according to claim 1, wherein the auxiliary medium circuit cools the utilization air by supplying the auxiliary medium cooled by the auxiliary medium heat exchanger to the auxiliary medium tube.
14. The refrigerant circuit includes an outdoor refrigerant heat exchanger (216) that exchanges heat between the unused air (AR) and the low-pressure refrigerant and absorbs heat by the low-pressure refrigerant,
    The heat utilization system according to claim 13, wherein the auxiliary medium heat exchanger (243) cools the auxiliary medium with the low-pressure refrigerant or the unused air (AR) in the outdoor refrigerant heat exchanger.
15. The refrigerant circuit includes a cycle switching device (15b, 213) that switches a flow path between a heating application and a cooling application,
    The outdoor refrigerant heat exchanger (216) exchanges heat between the unused air (AR) and the low-pressure refrigerant in the heating application, absorbs heat into the low-pressure refrigerant, and uses the unused air (AR) in the cooling application. The heat utilization system according to claim 14, wherein heat exchange is performed with the high-pressure refrigerant to dissipate heat from the high-pressure refrigerant.
16. The control device increases the flow rate of the auxiliary medium flowing in the auxiliary medium heat exchanger (243) in accordance with the performance degradation due to frost in the outdoor refrigerant heat exchanger (216), or the use side heat exchanger The heat utilization system according to claim 14 or 15, wherein an amount of heat given to the auxiliary medium heat exchanger is increased by increasing a heat load of (70, 370, 470).
17. Furthermore, a temperature sensor (23) for detecting the temperature in the use side heat exchanger is provided,
    17. The control device according to claim 1, wherein the control device controls the refrigerant circuit in the cooling application based on a temperature detected by the temperature sensor and controls the cooling water circuit based on a temperature detected by the temperature sensor. The heat utilization system according to any one of the above.
18. further,
    Non-use side heat exchanger (270) having a plurality of tubes (16a, 43a) arranged in a row along a direction (RD) intersecting with a flow direction (CD) of non-use air (AR) )
    The tube
    A plurality of refrigerant tubes (16a) for exchanging heat between the low-pressure refrigerant and the unused air (AR) supplied from the refrigerant circuit, and the auxiliary medium and the unused air (AR) supplied from the auxiliary medium circuit 18, and a plurality of auxiliary medium tubes (43 a) arranged so as to be able to transfer heat with the refrigerant tubes (16 a) in at least a part of the row. Heat utilization system.
19. further,
    Use side heat exchange for high pressure refrigerant having a plurality of tubes (16a, 43a) arranged in a row along a direction (RD) intersecting the flow direction (CD) of the use air (UR). A vessel (370),
    The tube
    A plurality of refrigerant tubes (16a) that exchange heat between the high-pressure refrigerant supplied from the refrigerant circuit and use air (UR), and the auxiliary medium and use air (UR) supplied from the auxiliary medium circuit. 19. The heat utilization system according to claim 18, comprising a plurality of auxiliary medium tubes (43 a) arranged to exchange heat and to be able to transfer heat with the refrigerant tubes (16 a) in at least a part of the row.
20. The heat utilization system according to any one of claims 1 to 19, wherein the refrigerant circuit supplies the high-pressure refrigerant to the refrigerant tube.
21. The heat utilization system according to any one of claims 1 to 20, wherein the utilization air is air for air conditioning.
22. The heat utilization system according to any one of claims 1 to 20, wherein the utilization air is air in a warehouse that can store articles.
23. After the power becomes available, the control device preferentially controls the temperature of the use air by the use side heat exchangers (70, 370, 470), and the heat generating devices (HS, BT) by the auxiliary medium circuit. The heat utilization system according to claim 2, wherein the temperature control is performed.
24. The utilization device includes a battery charged by an external power source,
    The control device executes temperature control of the battery by the auxiliary medium circuit in preference to temperature control of the use air by the use side heat exchanger (70, 370, 470) when the battery is charged. The heat utilization system according to claim 2.

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