JP6044285B2 - Heat pump cycle - Google Patents

Description

  The disclosed invention relates to a heat pump cycle.

  Patent Document 1 discloses a heat pump cycle and defrosting control of the evaporator. Patent Document 2 to Patent Document 5 disclose a heat exchanger capable of flowing a plurality of media.

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

  In the technique of Patent Document 1, defrosting is performed using waste heat of the internal combustion engine. However, there is little waste heat in recent internal combustion engines. For this reason, a sufficient amount of heat for defrosting may not be obtained. In addition, in an electric vehicle such as a hybrid vehicle or an electric vehicle, there is little waste heat from the internal combustion engine, and less waste heat from electrical equipment such as an electric motor. For this reason, a sufficient amount of heat for defrosting may not be obtained.

  Moreover, from another viewpoint, in the technique of Patent Document 1, sufficient consideration is given to suppressing frost adhesion and growth before frost adheres to the extent that defrosting is necessary, that is, frost suppression. Not. Therefore, the prior art needed improvement in the stage of frost control.

  The heat exchanger disclosed in Patent Literature 2 to Patent Literature 5 can be used for defrosting. However, they do not disclose a heat pump cycle that can adequately utilize limited heat sources for frost control and / or defrosting.

  The disclosed invention has been made in view of the above problems, and an object thereof is to provide a heat pump cycle in which frost suppression and / or defrosting performance is improved.

  Another object of the disclosed invention is to provide a heat pump cycle that can effectively use a heat source for frost control and / or defrosting.

  Still another object of the disclosed invention is to provide a heat pump cycle suitable for use of the heat exchanger proposed by the inventors in Japanese Patent Application No. 2011-123199 or Japanese Patent Application No. 2011-82759.

  The disclosed invention employs the following technical means to achieve the above object.

The invention according to claim 1 is a compressor (11) for supplying high-pressure refrigerant by sucking and compressing low-pressure refrigerant, and a use-side heat exchange in which high-pressure refrigerant is supplied and heat is supplied from the high-pressure refrigerant. , A pressure reducer (13, 213) that depressurizes the high-pressure refrigerant and supplies a low-pressure refrigerant, and an endothermic heat exchanger (16) that causes the low-pressure refrigerant to absorb heat by exchanging heat between the air (AR) and the low-pressure refrigerant. And an auxiliary heat exchanger (43) disposed adjacent to the endothermic heat exchanger and supplying heat to the endothermic heat exchanger, and an auxiliary medium circuit (40) for circulating the auxiliary medium to the auxiliary heat exchanger A heat source device (HS, BT) for supplying heat to the auxiliary medium, a flow rate regulator (41, 42, 44, 45, 442) for adjusting the flow rate of the auxiliary medium supplied to the auxiliary heat exchanger, and endothermic heat A heat pump that absorbs heat from the exchanger and supplies heat to the user-side heat exchanger And a controller (100) for controlling the flow rate regulator so as to change the flow rate according to the progress of rolling, and the endothermic heat exchanger (16) and the auxiliary heat exchanger (43) are handled as an integral unit. The endothermic heat exchanger (16) includes a plurality of low temperature medium tubes (16a), and the auxiliary heat exchanger (43) includes a plurality of high temperature medium tubes (43a). And the cold medium tube and the hot medium tube are thermally coupled to each other in at least a part of the heat exchanger unit (70). Arranged in at least an upstream row and a downstream row with respect to the direction, the at least one hot medium tube being upstream of itself in the air flow direction and in the air flow direction. Without having low temperature medium tubes to overlap I, and, with respect to the direction perpendicular to the flow direction of the air, it is disposed adjacent to the low temperature medium tubes, the low temperature medium tubes and the high temperature medium tube, the upstream row It is characterized by being alternately arranged in at least a part of .

Since the auxiliary medium supplied to the auxiliary heat exchanger supplies heat to the endothermic heat exchanger, pumping of heat, that is, heat pump is promoted. Moreover, the auxiliary | assistant medium supplied to an auxiliary | assistant heat exchanger suppresses adhesion of the frost resulting from an endothermic heat exchanger directly or indirectly. When the flow rate is large, the effect of promoting the heat pump and the effect of suppressing frost formation are large. When the flow rate is low, heat is stored in the auxiliary medium circuit. The heat stored in the auxiliary medium circuit can be used for promoting a heat pump, suppressing frost adhesion, or defrosting. According to this configuration, the flow rate of the auxiliary medium supplied to the auxiliary heat exchanger is changed as the heat pump operation progresses. For this reason, promotion of a heat pump, suppression of frost formation, and the improvement of defrosting performance are achieved during the period of heat pump operation. According to this structure, an endothermic heat exchanger and an auxiliary heat exchanger can be provided by a heat exchanger unit that can be handled as an integral unit. According to this configuration, since the low temperature medium tube and the high temperature medium tube are thermally coupled, it is easy to supply the heat of the high temperature medium tube to the vicinity of the low temperature medium tube. According to this configuration, the high-temperature medium tube is disposed facing the upstream side in the air flow direction in the heat exchanger unit. For this reason, the heat of the hot medium tube is transmitted to the upstream side of the heat exchanger unit. This arrangement of hot media tubes provides an additional advantage by providing fins with louvers. This additional advantage is provided by a frost resistant edge formed on the fin. According to this configuration, heat exchange between the low temperature medium tube and the high temperature medium tube can be promoted in the upstream row.

The invention according to claim 2 is characterized in that the high-temperature medium tube is not located upstream of the heat exchanger unit (70) .

The invention described in claim 3 is characterized in that the cold medium tube and the hot medium tube have different widths in the air flow direction .

The invention according to claim 4 is characterized in that the low-temperature medium tube and the high-temperature medium tube are thermally coupled to each other through fins (50) for exchanging heat with air. According to this configuration, a thermal bond between the cold media tube and the hot media tube is provided through the fins. Therefore, the heat of the hot medium tube can be reliably supplied to the cold medium tube.

The invention according to claim 5 is a compressor (11) for supplying high-pressure refrigerant by sucking and compressing low-pressure refrigerant, and a use-side heat exchange in which high-pressure refrigerant is supplied and heat is supplied from the high-pressure refrigerant. , A pressure reducer (13, 213) that depressurizes the high-pressure refrigerant and supplies a low-pressure refrigerant, and an endothermic heat exchanger (16) that causes the low-pressure refrigerant to absorb heat by heat exchange between the air (AR) and the low-pressure refrigerant. And an auxiliary heat exchanger (43) disposed adjacent to the endothermic heat exchanger and supplying heat to the endothermic heat exchanger, and an auxiliary medium circuit (40) for circulating the auxiliary medium to the auxiliary heat exchanger A heat source device (HS, BT) for supplying heat to the auxiliary medium, a flow rate regulator (41, 42, 44, 45, 442) for adjusting the flow rate of the auxiliary medium supplied to the auxiliary heat exchanger, and endothermic heat A heat pump that absorbs heat from the exchanger and supplies heat to the user-side heat exchanger And a controller (100) for controlling the flow rate regulator so as to change the flow rate according to the progress of rolling, and the endothermic heat exchanger (16) and the auxiliary heat exchanger (43) are handled as an integral unit. The endothermic heat exchanger (16) includes a plurality of low temperature medium tubes (16a), and the auxiliary heat exchanger (43) includes a plurality of high temperature medium tubes (43a). And the cold medium tube and the hot medium tube are thermally coupled to each other in at least a part of the heat exchanger unit (70). It is arranged so as to constitute at least an upstream row and a downstream row with respect to the direction, and the cold medium tubes and the hot medium tubes are alternately arranged in at least a part of the upstream row. The features. Since the auxiliary medium supplied to the auxiliary heat exchanger supplies heat to the endothermic heat exchanger, pumping of heat, that is, heat pump is promoted. Moreover, the auxiliary | assistant medium supplied to an auxiliary | assistant heat exchanger suppresses adhesion of the frost resulting from an endothermic heat exchanger directly or indirectly. When the flow rate is large, the effect of promoting the heat pump and the effect of suppressing frost formation are large. When the flow rate is low, heat is stored in the auxiliary medium circuit. The heat stored in the auxiliary medium circuit can be used for promoting a heat pump, suppressing frost adhesion, or defrosting. According to this configuration, the flow rate of the auxiliary medium supplied to the auxiliary heat exchanger is changed as the heat pump operation progresses. For this reason, promotion of a heat pump, suppression of frost formation, and the improvement of defrosting performance are achieved during the period of heat pump operation. According to this structure, an endothermic heat exchanger and an auxiliary heat exchanger can be provided by a heat exchanger unit that can be handled as an integral unit. According to this configuration, since the low temperature medium tube and the high temperature medium tube are thermally coupled, it is easy to supply the heat of the high temperature medium tube to the vicinity of the low temperature medium tube. According to this configuration, heat exchange between the low temperature medium tube and the high temperature medium tube can be promoted in the upstream row.

The invention according to claim 6 is characterized in that the low-temperature medium tube and the high-temperature medium tube are thermally coupled via fins (50) for exchanging heat with air. According to this configuration, a thermal bond between the cold media tube and the hot media tube is provided through the fins. Therefore, the heat of the hot medium tube can be reliably supplied to the cold medium tube .

  According to a seventh aspect of the present invention, there is provided a flow path cross-sectional area for an endothermic heat exchanger provided by a plurality of low temperature medium tubes. It is characterized by being larger than the area. The effect of improving the performance by expanding the flow path area is greater in the endothermic heat exchanger than in the auxiliary heat exchanger. According to this structure, it can contribute to the performance improvement of a heat exchanger unit by the performance improvement of an endothermic heat exchanger.

  According to an eighth aspect of the present invention, the flow rate regulator includes a bypass passage (44) for bypassing the auxiliary heat exchanger and allowing the auxiliary medium to flow, and a flow rate flowing to the auxiliary heat exchanger by flowing the auxiliary medium to the bypass passage. And a valve device (42, 45, 442) for decreasing. According to this configuration, it is possible to selectively or simultaneously perform the supply of the auxiliary medium to the auxiliary heat exchanger and the heat storage to the auxiliary medium while circulating the auxiliary medium in the auxiliary medium circuit.

  The invention according to claim 9 is characterized in that the control device reduces the flow rate in accordance with the progress of the heat pump operation. According to this configuration, the effects of promoting the heat pump and suppressing the adhesion of frost are greatly exhibited in the initial stage of the heat pump operation. Thereafter, heat storage in the auxiliary medium is performed, so that the defrosting performance is improved.

  The invention described in claim 10 is characterized in that the control device decreases the flow rate in accordance with a decrease in the heat load of the heat pump operation. According to this configuration, the flow rate decreases as the heat load decreases. For this reason, the effect of promotion of a heat pump and suppression of adhesion of frost is exhibited largely in the initial stage of heat pump operation. Thereafter, heat storage in the auxiliary medium is performed, so that the defrosting performance is improved. For example, when heat pump operation is used for heating, the flow rate is reduced as the room temperature increases.

  In the invention according to claim 11, the control device reaches the boundary between rapid heating and stable heating indicated by the temperature (Rth, Tset) or time (t0-t1) of the air heated by the use side heat exchanger. It is characterized in that a large flow rate (Gr2) is supplied before starting and a limit flow rate (Grs, Gr1) less than the large flow rate is supplied after reaching the boundary. According to this structure, promotion of a heat pump and suppression of frost adhesion are achieved in rapid heating. Thereafter, heat is stored in the auxiliary medium in stable heating.

  The invention according to claim 12 is characterized in that the control device increases the flow rate in accordance with the progress of the heat pump operation. According to this configuration, heat storage to the auxiliary medium is performed at the initial stage of the heat pump operation, so that the defrosting performance can be improved. Thereafter, the effects of promoting the heat pump and suppressing the adhesion of frost are greatly exhibited.

  The invention described in claim 13 is characterized in that the control device increases the flow rate in accordance with an increase in the amount of frost on the endothermic heat exchanger. According to this configuration, the flow rate increases as the amount of frost formation increases. For this reason, heat storage to the auxiliary medium is performed at the initial stage of the heat pump operation. Thereafter, the effects of promoting the heat pump and suppressing the adhesion of frost are greatly exhibited. For example, the amount of frost formation can be known from the temperature or pressure of the refrigerant at the outlet of the endothermic heat exchanger. Since the refrigerant temperature or the refrigerant pressure decreases with an increase in the amount of frost formation, the flow rate can be increased with a decrease in the refrigerant temperature or the refrigerant pressure.

  In the invention according to claim 14, the control device increases the flow rate in response to temperature (Tp, TAO) or time (t0-t3) indicating an increase in the amount of frost on the endothermic heat exchanger (+ Grfb). It is characterized by that. According to this structure, the capability shortage by the increase in the amount of frost formation of an endothermic heat exchanger can be suppressed.

  The invention described in claim 15 is characterized in that the control device increases the flow rate in accordance with a decrease in the refrigerant temperature or refrigerant pressure of the endothermic heat exchanger. When the amount of frost formation increases, the refrigerant temperature or the refrigerant pressure decreases. Therefore, flow control according to the amount of frost formation becomes possible.

  According to a sixteenth aspect of the present invention, the control device increases the flow rate when the temperature (Tw) of the auxiliary medium increases. According to this configuration, when the temperature of the auxiliary medium rises, the flow rate to the auxiliary heat exchanger increases. Therefore, the amount of heat released from the auxiliary medium increases. As a result, the temperature of the auxiliary medium, that is, the temperature control of the heat source is realized.

  According to a seventeenth aspect of the present invention, the control device has a flow rate when the temperature (Tw) of the auxiliary medium is higher than the predetermined temperature (Wth1, Wth2), and the temperature (Tw) of the auxiliary medium is the predetermined temperature (Wth1, Wth2). It is characterized in that the flow rate is increased from the lower flow rate (+ Grfb). According to this configuration, the temperature of the auxiliary medium is controlled so that the temperature of the heat source is controlled to a temperature corresponding to the predetermined temperature.

  In the invention described in claim 18, the control device determines the flow rate after determining that the endothermic heat exchanger needs to be defrosted from the flow rate before determining that the endothermic heat exchanger needs to be defrosted. Increase (+ Grfb). According to this configuration, the flow rate is increased so as to defrost the endothermic heat exchanger.

  According to the nineteenth aspect of the present invention, after the controller reaches the boundary, the flow rate is responsive to temperature (Tp, TAO) or time (t0-t3) indicating an increase in the amount of frost formation on the endothermic heat exchanger. Is increased (+ Grfb).

  According to a twentieth aspect of the present invention, the control device sets the flow rate when the temperature (Tw) of the auxiliary medium is higher than the predetermined temperature (Wth1, Wth2) after the boundary is reached, and the temperature (Tw) of the auxiliary medium is predetermined. It is characterized by increasing (+ Grfb) from the flow rate when the temperature is lower than (Wth1, Wth2).

  The invention according to claim 21 is that the control device needs to defrost the endothermic heat exchanger after determining that it is necessary to defrost the endothermic heat exchanger after reaching the boundary. It is characterized by increasing the flow rate before the determination (+ Grfb).

  According to a twenty-second aspect of the present invention, the controller controls the flow rate regulator to supply the auxiliary medium to the auxiliary heat exchanger in order to defrost the frost adhering to the endothermic heat exchanger after the end of the heat pump operation. It is characterized by controlling. According to this structure, the frost adhering to the endothermic heat exchanger is defrosted by the heat stored in the auxiliary medium. And defrosting is performed after completion | finish of a heat pump driving | operation. Therefore, the influence of frost can be suppressed at the start of the next heat pump operation.

  The invention described in claim 23 further includes a hot gas device (14, 15a, 213) for introducing a high-pressure refrigerant into the endothermic heat exchanger, and the control device can perform endothermic heat exchange when the auxiliary medium alone cannot defrost. The hot gas equipment is controlled so as to introduce a high-pressure refrigerant into the vessel. According to this configuration, the high-pressure refrigerant is introduced into the endothermic heat exchanger when defrosting cannot be performed using only the auxiliary medium. For this reason, defrosting is possible without depending only on the heat storage to an auxiliary | assistant medium.

  Note that the reference numerals in parentheses described in the claims and the above-described means indicate correspondence with specific means described in the embodiments described later as one aspect, and It does not limit the technical scope.

It is a block diagram which shows the flow path at the time of heating operation of the heat pump cycle of 1st Embodiment of the disclosed invention. It is a block diagram which shows the flow path at the time of the defrost operation by the heat source of 1st Embodiment. It is a block diagram which shows the flow path at the time of the waste heat recovery driving | operation of 1st Embodiment. It is a block diagram which shows the flow path at the time of the air_conditionaing | cooling operation of 1st Embodiment. It is a flowchart which shows the defrost control of 1st Embodiment. 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. It is sectional drawing which shows the VIII-VIII cross section of FIG. It is a perspective view which shows the flow of the fluid in the heat exchanger of 1st Embodiment. It is sectional drawing which shows the XX cross section of FIG. It is a flowchart which shows control of the cooling water circuit of 1st Embodiment. It is a time chart which shows progress of heat pump operation of a 1st embodiment. It is a flowchart which shows the defrost control during parking of 1st Embodiment. It is a block diagram which shows the flow path at the time of heating operation of the heat pump cycle of 2nd Embodiment of the disclosed invention. It is a block diagram which shows the flow path at the time of the defrost operation by the refrigerant circuit of the heat pump cycle of 3rd Embodiment of the disclosed invention. It is a flowchart which shows the defrost control during parking of 3rd Embodiment. It is a block diagram which shows the flow path at the time of heating operation of the heat pump cycle of 4th Embodiment of the disclosed invention. It is a flowchart which shows control of the cooling water circuit of 4th Embodiment. It is a time chart which shows progress of heat pump operation of a 4th embodiment. It is a block diagram which shows the flow path at the time of the defrost operation which used together the refrigerant circuit and cooling water circuit of the heat pump cycle of 5th Embodiment of the disclosed invention. It is a flowchart which shows the defrost control during parking of 5th Embodiment. It is a flowchart which shows the defrost control during parking of 6th Embodiment of the disclosed invention. It is a flowchart which shows the defrost control during parking of 7th Embodiment of the disclosed invention. It is a flowchart which shows the defrost control during parking of 8th Embodiment of the disclosed invention. It is a block diagram which shows the cooling water circuit of 9th Embodiment of the disclosed invention. It is a flowchart which shows the defrost control during parking of 9th Embodiment of the disclosed invention. It is a block diagram which shows the cooling water circuit of 10th Embodiment of the disclosed invention. It is a block diagram which shows the cooling water circuit of 11th Embodiment of the disclosed invention. It is a block diagram which shows the cooling water circuit of 12th Embodiment of the disclosed invention. It is a block diagram which shows the cooling water circuit of 13th Embodiment of the disclosed invention. It is a block diagram which shows the cooling water circuit of 14th Embodiment of disclosed invention. It is a block diagram which shows the cooling water circuit of 15th Embodiment of the disclosed invention. It is a block diagram which shows the cooling water circuit of 16th Embodiment of the disclosed invention. It is a block diagram which shows the cooling water circuit of 17th Embodiment of the disclosed invention. It is a flowchart which shows control of the cooling water circuit of 18th Embodiment of disclosed invention. It is a time chart which shows progress of heat pump operation of an 18th embodiment. It is sectional drawing which shows the heat exchanger of 1st Embodiment corresponded to FIG. It is sectional drawing which shows the heat exchanger of 19th Embodiment of the disclosed invention. It is sectional drawing which shows the heat exchanger of 20th Embodiment of the disclosed invention. It is sectional drawing which shows the heat exchanger of 21st Embodiment of the disclosed invention. It is sectional drawing which shows the heat exchanger of 22nd Embodiment of disclosed invention. It is sectional drawing which shows the heat exchanger of 23rd Embodiment of the disclosed invention. It is sectional drawing which shows the heat exchanger of 24th Embodiment of the disclosed invention. It is sectional drawing which shows the heat exchanger of 25th Embodiment of the disclosed invention.

  Hereinafter, a plurality of modes for carrying out the disclosed 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. 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 air conditioner 1 for a vehicle is provided according to one embodiment of the disclosed invention. 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 70 to which the disclosed invention is applied. The heat pump cycle 2 includes a refrigerant circuit 10 and a cooling water circuit 40.

  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 heat pump cycle 2 uses at least one of an engine, a motor generator, an inverter circuit, a battery, a control circuit, and the like of the hybrid vehicle as an external heat source HS. As the external heat source HS, one of in-vehicle devices that generate heat during operation can be used. The external heat source HS supplies heat to the auxiliary medium, that is, the cooling water WT. The cooling water circuit 40 is also a cooling system for cooling the external heat source HS and keeping it at an appropriate temperature. 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. In recent vehicles, there is little waste heat supplied from a power source. For this reason, if it relies only on the waste heat from the power source, it is difficult to suppress frost and / or defrost the outdoor heat exchanger 16. This embodiment provides a heat pump cycle 2 that can effectively use waste heat from a power source to suppress frost on the outdoor heat exchanger 16 and / or perform defrosting.

  The air conditioner 1 is a device that uses heat pumped from air by the heat pump cycle 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. The air conditioner 1 includes a control device (CNTR) 100 that controls the heat pump cycle 2 and the air conditioning unit 30.

  The air conditioning unit 30 is disposed in the vehicle interior. 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 indoor condenser 12, and the indoor evaporator 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.

  On the downstream side of the blower 32, the indoor evaporator 20 and the indoor condenser 12 are arranged in this order with respect to the flow of the air UR. The indoor evaporator 20 is disposed on the upstream side with respect to the indoor condenser 12. The indoor evaporator 20 is a cooling heat exchanger that exchanges heat between the refrigerant circulating in the interior and the air UR to cool the air UR. 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.

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

  The refrigerant circuit 10 is provided by a vapor compression refrigeration cycle capable of reversible operation. The refrigerant circuit 10 is a refrigerant cycle for heating the air conditioner 1. The refrigerant circuit 10 can additionally serve as 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 is also called a refrigerant system. 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 16 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 16 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 vehicle interior. 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 16 during the heating operation. Furthermore, the refrigerant circuit 10 can execute a waste heat recovery operation in which the heat of the external heat source HS is absorbed by the refrigerant during the heating operation. The plurality of operation modes are switched by the control device 100.

  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 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.

  A fixed throttle 13 for heating is provided downstream of the indoor condenser 12. The fixed throttle 13 decompresses and expands the refrigerant that has flowed out of the indoor condenser 12 during the heating operation. The fixed throttle 13 is a decompression means for heating operation. The fixed throttle 13 can be provided by an orifice, a capillary tube, or the like. The fixed throttle 13 provides a decompressor that decompresses the high-pressure refrigerant and supplies the low-pressure refrigerant. An outdoor heat exchanger 16 is provided downstream of the fixed throttle 13. Furthermore, a passage 14 for bypassing the fixed throttle 13 is provided downstream of the indoor condenser 12. The passage 14 guides the refrigerant flowing out of the indoor condenser 12 to the outdoor heat exchanger 16 by bypassing the fixed throttle 13. An opening / closing valve 15 a that opens and closes the passage 14 is disposed in the passage 14. The on-off valve 15a is an electromagnetic valve. The pressure loss in the on-off valve 15 a is sufficiently smaller than the pressure loss in the fixed throttle 13. Therefore, when the on-off valve 15a is open, the refrigerant flows exclusively through the passage 14. On the other hand, when the on-off valve 15 a is closed, the refrigerant flows through the fixed throttle 13. Thereby, the on-off valve 15a switches the flow path of the refrigerant circuit 10. The on-off valve 15a functions as a refrigerant channel switching means. The switching means may be provided by an electric three-way valve.

  The outdoor heat exchanger 16 exchanges heat between the low-pressure refrigerant flowing inside and the air AR. The outdoor heat exchanger 16 is disposed in the engine room. The outdoor heat exchanger 16 functions as an evaporator that evaporates low-pressure refrigerant and exerts an endothermic effect during heating operation. The outdoor heat exchanger 16 provides an endothermic heat exchanger that exchanges heat between the air AR and the low-pressure refrigerant and causes the low-pressure refrigerant to absorb heat. The outdoor heat exchanger 16 functions as a radiator that radiates high-pressure refrigerant during cooling operation. The outdoor heat exchanger 16 is configured integrally with the radiator 43. The outdoor heat exchanger 16 and the radiator 43 constitute a heat exchanger 70. The heat exchanger 70 is a heat exchanger unit that can be handled as an integral unit.

  The cooling water WT flows through the radiator 43. The radiator 43 exchanges heat between the cooling water WT of the cooling water circuit 40 and the air AR. Furthermore, the radiator 43 supplies the heat of the cooling water WT to the outdoor heat exchanger 16 and the heat exchanger 70 including the same. The radiator 43 stores an auxiliary medium that stores heat and supplies the stored heat to the endothermic heat exchanger, that is, the cooling water WT. The radiator 43 provides an auxiliary heat exchanger disposed adjacent to the outdoor heat exchanger 16.

  The fan 17 is an electric blower that blows air AR to the outdoor heat exchanger 16. The fan 17 provides an outdoor blower that blows the air AR toward both the outdoor heat exchanger 16 and the radiator 43.

  An electrical three-way valve 15 b is connected downstream of the outdoor heat exchanger 16. The three-way valve 15b is controlled by the control device 100. The three-way valve 15b, together with the on-off valve 15a, constitutes a refrigerant channel switching means. The three-way valve 15b directly connects the outlet of the outdoor heat exchanger 16 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 16 and the inlet of the fixed throttle 19 during cooling operation. The fixed throttle 19 is a pressure reducing means for cooling. The fixed throttle 19 decompresses and expands the refrigerant that has flowed out of the outdoor heat exchanger 16 during the cooling operation. The fixed diaphragm 19 has the same configuration as the fixed diaphragm 13.

  An indoor evaporator 20 is provided downstream of the fixed throttle 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 16 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 is a heat source device that supplies heat to the refrigerant circuit 10. The cooling water circuit 40 can flow cooling water WT used as a heat carrying medium and a heat storage medium. The cooling water circuit 40 including the external heat source HS is called a water system or an external heat source system. 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 device 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 device 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 external heat source HS at a temperature higher than the temperature at which the refrigerant in the refrigerant tube 16a absorbs heat.

  The coolant circuit 40 is a coolant circulation circuit that circulates coolant through the external heat source HS and cools the external heat source HS. The cooling water circuit 40 includes components such as a pump 41, an electric three-way valve 42, a radiator 43, and a bypass passage 44 for bypassing the radiator 43 and flowing cooling water. The pump 41 is an electric pump that pumps cooling water to the cooling water circuit 40.

  The three-way valve 42 switches the flow path in the cooling water circuit 40. The three-way valve 42 switches between a flow path that passes through the external heat source HS and the radiator 43 and a flow path that passes through the external heat source HS and the bypass passage 44. The bypass passage 44 provides a flow path that bypasses the radiator 43. The pump 41, the three-way valve 42, and the bypass passage 44 provide a flow rate regulator that regulates 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 42 that reduces the flow rate flowing through the radiator 43 by flowing the cooling water WT through the bypass passage 44.

  When the cooling water WT is caused to flow through the bypass passage 44 by the three-way valve 42 and bypass the radiator 43, the cooling water WT increases its temperature without releasing heat from the radiator 43. In other words, heat is stored in the cooling water WT at this time. The radiator 43 is a heat exchanger for heat dissipation that is disposed in the engine room and exchanges heat between the cooling water WT and the air AR blown from the fan 17. The radiator 43 is configured integrally with the outdoor heat exchanger 16 and constitutes a heat exchanger 70. When the cooling water is caused to flow through the radiator 43 by the three-way valve 42, the cooling water WT is radiated by the radiator 43. The cooling water WT gives heat to the air UR and / or the refrigerant. At this time, the heat given from the high-temperature refrigerant to the cooling water WT by the heat exchanger 80 is given to the heat exchanger 70 in the radiator 43.

  The heat exchanger 70 provides heat exchange between the refrigerant RF, the cooling water WT, and the air AR. The heat exchanger 70 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 70 has components such as a plurality of tubes through which refrigerant or cooling water flows, a collection tank and a distribution tank disposed at both ends of the plurality of tubes.

  The outdoor heat exchanger 16 has a plurality of refrigerant tubes 16a through which refrigerant flows. The refrigerant tube 16a is a heat exchange tube through which the refrigerant RF that absorbs heat from the air flows. The refrigerant tube 16a is also called a low temperature medium tube through which the low temperature medium CMD flows during heating operation. The refrigerant tube 16a is a flat tube having a flat cross-sectional shape perpendicular to the longitudinal direction.

  The radiator 43 has a plurality of water tubes 43a through which cooling water flows. The water tube 43a is a heat exchange tube through which a medium for frost suppression and / or defrosting is passed. The water tube 43a is also referred to as a high-temperature medium tube through which the high-temperature medium HMD flows during heating operation and defrosting operation. The heat of the high-temperature medium HMD suppresses frost formation on the heat exchanger 70 during the heating operation. Furthermore, the heat of the high-temperature medium HMD melts the frost on the heat exchanger 70 during the defrosting operation. 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 their wide flat surfaces are substantially parallel to the flow of the air AR. 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 AR flows are formed around the plurality of tubes 16a and 43a. The air passages 16b and 43b are used as heat dissipation air passages and / or heat absorption air passages.

  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 plurality of tubes 16a and 43a are arranged in a row in a direction orthogonal to the flow of the air AR. Further, the plurality of tubes 16a and 43a are arranged in multiple rows along the flow direction of the air AR. As illustrated, 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 located upstream in the flow direction of the air AR and a downstream row located downstream from the upstream row.

  In at least a part of the upstream row, the refrigerant tube 16a and the water tube 43a are adjacent to each other. In the upstream row, at least in part, the water tubes 43a can be positioned on both sides of the refrigerant tube 16a. In the upstream row, at least in part, the refrigerant tubes 16a can be positioned on both sides of the water tube 43a. In at least a part of the upstream row, the refrigerant tubes 16a and the water tubes 43a can be alternately positioned. 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 at least in the upstream row. That is, in the heat exchanger 70, on the air AR inflow side, the water tubes 43a are positioned on both sides of the refrigerant tube 16a, and they are arranged side by side.

  According to this configuration, the refrigerant tubes can be dispersed in a wide range. As a result, frost can be dispersed over a wide range. Furthermore, the water tube 43a is located next to the refrigerant tube 16a. For this reason, during heating operation, frost adhesion and frost growth in the vicinity of the refrigerant tube 16a can be suppressed. In addition, during the defrosting operation, the heat supplied from the water tube 43a can be efficiently transmitted to the frost mass grown in the vicinity of the refrigerant tube 16a.

  In the downstream row, the refrigerant tubes 16a and the water tubes 43a can be arranged in the same manner as in the upstream row. Instead, only the refrigerant tube 16a or only the water tube 43a may be arranged in the downstream row.

  The plurality of tubes 16a and 43a can be arranged such that a large number of water tubes 43a are located in the upstream row and a small number of water tubes 43a are located in the downstream row. Further, the plurality of tubes 16a and 43a can be arranged such that the water tube 43a is located only in the upstream row. Thus, a configuration is provided in which the radiator 43 is mainly disposed on the upstream side of the flow of the air AR, and the outdoor heat exchanger 16 is mainly disposed on the downstream side.

  Fins 50 are arranged 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 AR. 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 AR. Therefore, at least four tubes 16 a and 43 a are joined to one fin 50. The fin 50 integrates the outdoor 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 AR. The fin 50 promotes heat exchange between the cooling water WT and the air AR. 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 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.

  The tank of the outdoor 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.

  The heat exchanger 70 includes a core portion in which the tubes 16a and 43a and the fins 50 are disposed, and tank portions disposed at both ends of the core portion. The tubes 16a and 43a arranged in the core portion constitute a plurality of rows including at least an upstream row and a downstream row with respect to the flow direction of the air AR. Each of the two tank parts has an inner tank adjacent to the core part and an outer tank located away from the core part. The inner tank and the outer tank extend so as to cover almost the entire end of the core at the end of the core. Therefore, the inner tank and the outer tank are stacked on one end of the core portion. An inner tank and an outer tank are also stacked on the other end of the core portion. Some of the plurality of tubes 16a and 43a are connected so as to communicate with the inside of the inner tank, and the remaining portions of the plurality of tubes 16a and 43a are connected so as to communicate with the inside of the outer tank. These remaining portions extend through the walls of the inner tank. The tubes 16a and 43b are arranged in a distributed manner inside the core portion. The tube 16a or the tube 43a can be arranged so as to form an uneven distribution inside the core portion. Arrangement | positioning of the tubes 16a and 43a in a core part is set so that the performance of the heat exchange requested | required of the outdoor heat exchanger 16 and the radiator 43 may be matched. The heat exchanger 70 enables a relatively free arrangement of the tubes 16a and 43a. For example, the tubes 16a or the tubes 43a are distributed and arranged in the upstream row and the downstream row along the flow direction of the air AR. In other words, the tubes 16a and the tubes 43a can be mixed in the upstream row or the downstream row.

  The control device 100 is provided by a microcomputer including 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, 15 a, 15 b, 17, 41, 42. A plurality of sensors are connected to the control device 100. The plurality of sensors include an inside air sensor as an inside air temperature detecting means for detecting the temperature in the vehicle interior, an outside air sensor for detecting the temperature of the outdoor air, a solar radiation sensor for detecting the amount of solar radiation in the vehicle interior, and a blowout of the indoor evaporator 20 An evaporator temperature sensor for detecting the air temperature (evaporator temperature) and a discharge refrigerant temperature sensor for detecting the compressor 11 discharge refrigerant temperature can be included. Furthermore, the plurality of sensors include an outlet refrigerant temperature sensor 51 that detects the outlet side refrigerant temperature Te of the outdoor heat exchanger 16, and a cooling water temperature detection unit that detects the cooling water temperature Tw flowing into the traveling electric motor MG. A coolant temperature sensor 52 may be included.

  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 controlled by controlling the devices 15a and 15b. 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 flow path of the cooling water is controlled by controlling the three-way valve 42.

  Furthermore, the control apparatus 100 provides frost determination means for determining whether or not frost formation has occurred in the outdoor heat exchanger 16 based on detection signals of a plurality of sensors and / or timers. In the frosting determination means, the vehicle speed of the running vehicle is lower than a predetermined reference vehicle speed, for example, 20 km / h, and the outdoor heat exchanger 16 outlet side refrigerant temperature Te is set to a predetermined reference temperature, for example, 0 ° C. When it falls below, it determines with the outdoor heat exchanger 16 having formed frost. The control device 100 provides a defrost control unit that performs defrost control for removing frost attached to the outdoor heat exchanger 16. The defrosting control unit controls the heat pump cycle 2.

  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 control device 100 controls the air conditioner 1 so that the air conditioner 1 selectively provides a cooling operation (COOL) or a heating operation. Further, the control device 100 controls the air conditioner 1 to provide a normal heating operation (HEAT1), a defrosting operation (HOT-WT), or a waste heat recovery operation (HEAT2) during the heating operation. If frost formation is determined by the frost determination means during the normal heating operation, the operation proceeds to the defrost operation. When a predetermined condition is satisfied during the normal heating operation, the operation shifts to the waste heat recovery operation. Further, when the return condition is satisfied, the normal heating operation is resumed.

(A) Normal heating operation (HEAT1)
During normal heating operation, the interior of the vehicle is heated by heating the air UR with the indoor condenser 12 using the air AR outside the vehicle as a heat source. The normal heating operation is activated by a switch operated by a vehicle user. The refrigerant circuit 10 is controlled such that the on-off valve 15a is closed, the three-way valve 15b connects the outdoor heat exchanger 16 and the accumulator 18 via the flow path 20a, and the compressor 11 is operated. Thereby, the refrigerant circuit 10 is switched to the refrigerant flow path through which the refrigerant flows as shown by the solid line arrows in FIG. The cooling water circuit 40 is controlled so that the pump 41 pumps cooling water at a predetermined flow rate, and the three-way valve 42 flows cooling water through the bypass passage 44. The cooling water circuit 40 is switched to a circuit through which the cooling water flows as shown by the broken-line arrows in FIG.

  In the refrigerant circuit 10 during normal heating operation, the high-pressure refrigerant discharged from the compressor 11 flows into the indoor condenser 12. The refrigerant flowing into the indoor condenser 12 exchanges heat with the air UR that is blown from the blower 32 and passes through the indoor evaporator 20 to dissipate heat. Thereby, the air UR is heated. Thereafter, the high-pressure refrigerant flows into the fixed throttle 13 and is decompressed and expanded.

  The low-pressure refrigerant decompressed and expanded by the fixed throttle 13 flows into the outdoor heat exchanger 16. The low-pressure refrigerant that has flowed into the outdoor heat exchanger 16 absorbs heat from the air AR blown by the fan 17 and evaporates. The refrigerant flowing out of the outdoor heat exchanger 16 flows into the accumulator 18 and is separated into gas and liquid. The gas-phase refrigerant separated by the accumulator 18 is sucked into the compressor 11 and compressed again.

  In the cooling water circuit 40, since the cooling water WT flows into the bypass passage 44, heat dissipation from the cooling water to the refrigerant and heat absorption from the refrigerant to the cooling water in the heat exchanger 70 are suppressed. In other words, the thermal mutual influence relationship between the cooling water and the refrigerant is suppressed. As a result, heat supplied from the external heat source HS is stored in the cooling water circuit 40.

(B) Defrosting operation (HOT-WT)
During the defrosting operation, the frost adhering to the outdoor heat exchanger 16 is released by the heat obtained from the cooling water circuit 40. In the defrosting operation, the control device 100 stops the operation of the compressor 11 and stops the operation of the fan 17. Therefore, during the defrosting operation, the refrigerant flow rate flowing into the outdoor heat exchanger 16 is reduced and the air volume of the air AR flowing into the heat exchanger 70 is reduced as compared with the normal heating operation. Furthermore, the control device 100 switches the three-way valve 42 so that the cooling water passes through the radiator 43 as indicated by the broken-line arrows in FIG. Accordingly, the heat of the cooling water flowing through the water tube 43 a of the radiator 43 is supplied to the heat exchanger 70. In particular, heat is transferred to the outdoor heat exchanger 16 through the fins 50 to defrost the outdoor heat exchanger 16. That is, defrosting that effectively uses the heat of the cooling water circuit 40 is realized. The heat used for defrosting includes waste heat supplied from the external heat source HS.

  The heat exchanger 70 is provided with fins 50 made of a metal member, and enables heat transfer between the refrigerant tube 16a and the water tube 43a. As a result, the heat of the cooling water can be transferred to the outdoor heat exchanger 16 through the fins 50 during the defrosting operation. As a result, it is possible to shorten the defrosting operation time.

  Further, by stopping the operation of the compressor 11 during the defrosting operation, the flow rate of the refrigerant flowing into the outdoor heat exchanger 16 is reduced, for example, 0 (zero) before the transition to the defrosting operation. Therefore, it can suppress that heat is absorbed into the refrigerant | coolant which distribute | circulates the refrigerant | coolant tube 16a. In other words, since the operation of the compressor 11 is stopped during the defrosting operation and the heat absorption amount of the refrigerant in the outdoor heat exchanger 16 is reduced, the heat of the cooling water circuit 40 including the external heat source HS is defrosted. Can be used effectively. Further, by stopping the operation of the fan 17 during the defrosting operation, the air volume of the air AR flowing into the heat exchanger 70 is reduced, for example, 0 (zero). Therefore, it can suppress that heat is absorbed into the air AR. Further, in the refrigerant circuit 10, the heat of the external heat source HS is stored in the cooling water circuit 40. Therefore, defrosting can be completed in a short time by the stored heat.

(C) Waste heat recovery operation (HEAT2)
During the waste heat recovery operation, the vehicle interior is heated using the external heat source HS as a heat source. The heat of the cooling water circuit 40 can be radiated to the air AR, but when a predetermined condition is satisfied, a waste heat recovery operation is performed to increase the heating capacity by passing the heat of the cooling water circuit 40 to the refrigerant circuit 10. The For example, when the cooling water temperature Tw exceeds a predetermined reference temperature, for example, 60 ° C. during the heating operation, the waste heat recovery operation can be executed.

  In the waste heat recovery operation, the three-way valve 15b is controlled similarly to the normal heating operation. The three-way valve 42 is controlled similarly to the defrosting operation. Therefore, as indicated by solid line arrows in FIG. 3, the high-pressure refrigerant discharged from the compressor 11 heats the air UR in the indoor condenser 12, flows into the heat exchanger 80, and heats the cooling water WT. Thereafter, the high-pressure refrigerant is decompressed and expanded by the fixed throttle 13 and flows into the outdoor heat exchanger 16. The low-pressure refrigerant flowing into the outdoor heat exchanger 16 absorbs both the heat of the air AR and the heat of the cooling water WT transferred through the fins 50 and evaporates. Thus, the cooling water circuit 40 supplies heat absorbed by the refrigerant RF that flows through the refrigerant tube 16a. According to this configuration, the heat absorption to the refrigerant RF of the refrigerant tube 16a is promoted by the cooling water WT flowing in the water tube 43a. As a result, a large amount of heat can be absorbed by the refrigerant RF in the refrigerant tube 16a. As a result, it is possible to realize heating that effectively uses the waste heat of the external heat source HS.

(D) Cooling operation (COOL)
During the cooling operation, the passenger compartment is cooled. The cooling operation is activated by a switch operated by a vehicle user. The refrigerant circuit 10 is controlled such that the on-off valve 15a is opened, the three-way valve 15b connects the outdoor heat exchanger 16 and the fixed throttle 19, and the compressor 11 is operated. The refrigerant flows through the refrigerant circuit 10 as indicated by solid line arrows in FIG. In the cooling water circuit 40, when the cooling water temperature Tw exceeds the reference temperature, the three-way valve 42 causes the cooling water to flow into the radiator 43, and when the cooling water temperature Tw falls below the reference temperature, the three-way valve 42 passes the cooling water to the bypass passage 44. Controlled to bypass. In FIG. 4, the flow of the cooling water when the cooling water temperature Tw exceeds the reference temperature is indicated by a broken line arrow.

  In the refrigerant circuit 10, the high-pressure refrigerant discharged from the compressor 11 flows into the indoor condenser 12, heats the air UR, flows into the heat exchanger 80, and heats the cooling water WT. Thereafter, the high-pressure refrigerant flows into the outdoor heat exchanger 16 through the passage 14. The high-pressure refrigerant that has flowed into the outdoor heat exchanger 16 further dissipates heat to the air AR blown by the fan 17. The refrigerant flowing out of the outdoor heat exchanger 16 is decompressed and expanded by the fixed throttle 19. The refrigerant flowing out from the fixed throttle 19 flows into the indoor evaporator 20 and absorbs heat from the air UR to evaporate. Thereby, the air UR is cooled. The refrigerant flowing out of the indoor evaporator 20 flows into the accumulator 18 and is separated into gas and liquid, and is sucked into the compressor 11 and compressed again.

  When the refrigerant circuit 10 is in cooling operation, that is, when the outdoor heat exchanger 16 functions as a condenser, the cooling water circuit 40 may be used as an auxiliary heat dissipation device that takes heat from the refrigerant circuit 10. For example, the flow rate of the cooling water WT flowing through the radiator 43 is maximized during the cooling operation. Thereby, discharge | release to the cooling water circuit 40 from the refrigerant circuit 10 is accelerated | stimulated, and the air_conditioning | cooling performance by the refrigerant circuit 10 can be improved.

  FIG. 5 is a flowchart showing the control for shifting to the defrost control executed during the heating operation. In step S100, it is determined whether frost is generated in the outdoor heat exchanger 16 and defrosting is performed. In step S200, the air conditioning mode of the air conditioning unit 30 is controlled so as to suppress a change in the air conditioning state during the defrosting control. In step S300, defrost control is executed. In step S300, the start of the defrost control and the completion of the defrost control are controlled. In step S400, the air conditioning unit 30 is returned to the air conditioning mode before the start of the defrosting operation. In step S500, it is determined whether or not a stop of the air conditioner 1 is requested. If the stop of the air conditioner 1 is not requested, the process returns to step S100, and if the stop of the air conditioner 1 is requested, the control is terminated.

  6-10, the heat exchanger 70 is what is called a tank and tube type heat exchanger. As shown in FIGS. 6 and 7, the refrigerant tubes 16a and the water tubes 43a are arranged in two rows along the flow direction of the air AR. The refrigerant tubes 16a and the water tubes 43a are alternately arranged in both the upstream row and the downstream row. 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. The fin 50 is joined to the tubes 16a and 43a adjacent thereto. A plurality of tubes 16a, tubes 43a, and a plurality of fins 50 are stacked and joined to form a heat exchange section. This heat exchange part provides heat exchange between a plurality of, for example, three fluids including the refrigerant RF, the cooling water WT, and the air AR.

  A first tank 16c for collecting or distributing refrigerant and cooling water is disposed at one end in the longitudinal direction of the plurality of tubes 16a and tubes 43a, and below in the drawing. The first tank is also referred to as a refrigerant tank because it accepts the refrigerant and discharges the refrigerant. The first tank also provides a connecting portion that guides cooling water from one water tube 43a to another 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. . 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.

  A portion of the intermediate plate member 162 corresponding to the refrigerant tube 16a is provided with a through hole 162a penetrating 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 space 163a for collecting refrigerant and a distribution space 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 collective space 163a and the distribution space 163b are partitioned as mutually independent spaces. A collecting space 163a is disposed on the upstream side of the air AR, and a distribution space 163b is disposed on the downstream side.

  Plate-shaped lid members are fixed to both longitudinal ends of the first tank member 163. One end of the distribution space 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 collective space 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 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 that guides the refrigerant from one refrigerant tube 16a to another refrigerant tube 16a.

  The second tank 43c has basically 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 a collecting space 433a for collecting cooling water and a distribution space 433b for distributing cooling medium. A distribution space 433b is disposed on the upstream side of the air AR, and a collective space 433a is disposed on the downstream side.

  Plate-shaped lid members are fixed to both ends of the second tank member 433 in the longitudinal direction. An inlet pipe 434 through which cooling water flows is connected to one end of the distribution space 433b. One end of the collective space 433a is connected to an outlet pipe 435 through which the refrigerant flows out.

  As shown in FIG. 8, a space CNC that provides a communication portion is formed between the intermediate plate members 162 and 432 and the connection plate members 161 and 431. The intermediate plate members 162 and 432 are formed with a plurality of recessed portions 162b and 432b. The plurality of recesses 162b and 432b are formed by the tubes 43a and 16a between the intermediate plate members 162 and 432 and the connection plate members 161 and 431 by fixing the intermediate plate members 162 and 432 to the connection plate members 161 and 431, respectively. A plurality of spaces CNC communicated with each other is formed. The space CNC formed between the intermediate plate member 162 and the connection plate member 161 allows two water tubes 43a arranged in two rows in the flow direction of the air AR to communicate with each other. A space CNC formed between the intermediate plate member 432 and the connection plate member 431 allows two refrigerant tubes 16a arranged in two rows in the flow direction of the air AR to communicate with each other.

  As shown in FIG. 9, the refrigerant RF and the cooling water WT flow as counterflows in most parts of the heat exchanger 70. Solid line arrows indicate the flow of the refrigerant RF. Dashed arrows indicate the flow of the cooling water WT.

  The refrigerant RF flows into the distribution space 163b of the first tank 16c through 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 refrigerant tube 16a in the downstream row flows into the refrigerant tube 16a in the upstream row through the space CNC 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 space 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 space 433b of the second tank 43c via the inlet pipe 434, and flows into the upstream water tube 43a. The cooling water flows from the top to the bottom in the drawing in the water tube 43a in the upstream row. The refrigerant that has flowed out of the upstream water tube 43a flows into the downstream water tube 43a through the space CNC of the first tank 16c. The cooling water flows from the bottom to the top of the water tube 43a in the downstream row. The cooling water that has flowed out of the water tube 43a in the downstream row flows out from the outlet pipe 435 after collecting in the collecting space 433a of the second tank 43c. Therefore, in the heat exchanger 70, the cooling water flows in a U-turn shape from the upstream row to the downstream row.

  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. This arrangement is effective for efficiently transferring the heat supplied from the water tube 43a to the frost growing in the vicinity of the refrigerant tube 16a. In at least a part of the upstream row 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 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. Furthermore, the refrigerant tubes 16a and the water tubes 43a can be alternately arranged in the downstream row.

  An air passage 16b for absorbing heat from the refrigerant tube 16a and an air passage 43b for radiating heat from the water tube 43a are provided by a common air passage. For this reason, the frost which grew in the vicinity of the refrigerant | coolant tube 16a can be efficiently defrosted with the heat of the water tube 43a.

  As shown in FIG. 10, the refrigerant tube 16 a allows the low-temperature medium CMD to flow during the heating operation. The low temperature medium CMD is a low pressure refrigerant in the refrigerant circuit 10. The water tube 43a flows a high-temperature medium HMD that is higher in temperature than the low-temperature medium CMD during the heating operation. The high temperature medium HMD is the cooling water WT in the cooling water circuit 40. Due to the low temperature medium CMD, frost adheres to the surfaces of the refrigerant tubes 16a and the fins 50 and tries to grow. However, since the high-temperature medium HMD flows through the water tube 43a, frost adhesion on the constituent members of the heat exchanger 70 such as the tubes 16a and 43a and the fins 50 and the growth of frost are suppressed during the heating operation. .

  Furthermore, also during the defrosting operation, the high-temperature medium HMD is caused to flow through the water tube 43a. The temperature of the high-temperature medium HMD at the time of the defrosting operation is a temperature at which the large frost mass is melted, for example, 60 ° C. or more. In addition, a sufficient amount of cooling water is supplied to the water tube 43a in order to supply an amount of heat necessary for melting the frost mass.

  In FIG. 11, the control device 100 adjusts the flow rate of the cooling water WT to the radiator 43 according to the heat load of the air conditioner 1 that is a heat utilization device in the heating operation. The control device 100 controls the three-way valve 42 so that the flow rate of the cooling water WT flowing through the radiator 43 increases as the heat load increases. Specifically, the control device 100 causes the cooling water WT to flow through the radiator 43 when the heat load exceeds a predetermined value and executes the waste heat recovery operation HEAT2, and when the heat load falls below the predetermined value, The cooling water WT is flowed to perform the normal heating operation HEAT1. The heat load is indicated by, for example, a difference between the temperature to be controlled and the target temperature.

  The control device 100 executes a control process S610 for controlling the cooling water circuit 40. Hereinafter, the step is expressed as S. In S611, it is determined whether the heat pump operation HP is in an ON state, that is, whether it is being executed. When the heat pump operation HP is being executed, the process proceeds to S612. In S612, the pump 41 is turned on. As a result, the cooling water WT flows in the cooling water circuit 40.

  In S613, external heat source control for adjusting the temperature of the external heat source HS is executed. Here, the cooling water temperature Tw is compared with a predetermined threshold temperature, and whether or not the cooling water TW is allowed to flow to the radiator 43 is switched. In S613, the amount of heat released from the radiator 43 is adjusted by adjusting the flow rate to the radiator 43 so that the cooling water temperature Tw is maintained in a predetermined temperature range. In S613, the coolant temperature Tw is compared with predetermined threshold temperatures Wth1 and Wth2. The threshold temperatures Wth1 and Wth2 provide hysteresis characteristics. The threshold temperature Wth1 is set lower than the threshold temperature Wth2. For example, when the external heat source HS is an inverter circuit in an electric vehicle, the threshold temperature Wth1 can be set within a range of 50 ° C to 60 ° C, and the threshold temperature Wth1 is within a range of 60 ° C to 65 ° C. Can be set to

  When the cooling water temperature Tw rises and exceeds the threshold temperature Wth1, the cooling water temperature Tw is lowered. Here, the process proceeds to S614 in order to increase the flow rate to the radiator 43. In S614, waste heat recovery operation HEAT2 is executed. Here, the three-way valve 42 is switched so that the cooling water WT flows only to the radiator 43, that is, the heat exchanger 70.

  If the cooling water temperature Tw falls below the threshold temperature Wth2 when the cooling water temperature Tw falls, the cooling water temperature Tw is raised. Here, in order to decrease the flow rate to the radiator 43, the process proceeds to subsequent S615 and S616.

  In S615, it is determined whether or not the heat load of the heat pump operation exceeds a predetermined value. In this embodiment, since heating is provided by heat pump operation, the heat load is an air conditioning load. The determination as to whether the air conditioning load exceeds a predetermined value is also a determination as to whether rapid heating is necessary. Here, it is determined whether or not the room temperature TR in the passenger compartment is below a predetermined threshold temperature Rth. The threshold temperature Rth can be a predetermined fixed value, a target temperature in the passenger compartment, or a temperature set based on the target temperature. When the room temperature TR is lower than the threshold temperature Rth (TR <Rth), that is, when the thermal load is large, the process proceeds to S614. In S614, since the cooling water WT is supplied to the radiator 43, the heat of the cooling water WT is supplied to the radiator 43, the heat exchanger 70, and the outdoor heat exchanger 16. Therefore, the heat pump operation is executed using the air AR and the cooling water WT as heat sources. As a result, heat pumping by the heat pump operation is promoted.

  When the room temperature TR does not fall below the threshold temperature Rth (TR> = Rth), the process proceeds to S615. In S615, the normal heating operation HEAT1 is executed. Here, the three-way valve 42 is switched so that the cooling water WT flows only into the bypass passage 44. Therefore, the heat pump operation is executed using only the air AR as a heat source.

  In S613, when the temperature Tw of the cooling water WT rises, the control device 100 increases the flow rate of the cooling water WT flowing through the radiator 43. According to this configuration, when the temperature of the cooling water WT rises, the flow rate to the radiator 43 increases. Therefore, the amount of heat released from the cooling water WT increases. As a result, the temperature of the cooling water WT, that is, the temperature control of the external heat source HS is realized.

  FIG. 12 shows changes in the heat pump heat quantity HPQ, the room temperature Tr, and the flow rate Gr of the cooling water WT passing through the radiator 43 after the heat pump operation is started. In the figure, the solid line indicates this embodiment EMB1. The broken line indicates the comparative example CMP. The heat pump operation is started at time t0. At this time, the room temperature Tr is lower than the threshold temperature Rth. Therefore, the control device 100 operates the refrigerant circuit 10 so that the room temperature Tr approaches the threshold temperature Rth, and further, the room temperature Tr is maintained at the threshold temperature Rth. The control device 100 adjusts the flow rate Gr to the maximum value Gr2. The refrigerant circuit 10 absorbs heat from the air AR and the cooling water WT and raises the room temperature. After time t0, the heat pump heat quantity HPQ rises rapidly. Correspondingly, the room temperature Tr also rises rapidly. As the room temperature Tr approaches the threshold temperature Rth, the heat pump heat quantity HPQ gradually decreases.

  When the room temperature Tr reaches the threshold temperature Rth at time t1, the flow rate Gr is adjusted to the minimum value Gr1. Here, the minimum value Gr1 can be 0 (zero) or a predetermined small flow rate. After time t1, the refrigerant circuit 10 absorbs heat mainly from the air AR. As a result, the heat pump heat quantity HPQ is stabilized to a value that maintains the room temperature Tr at the threshold temperature Rth.

  The comparative example CMP shows a case where the flow rate Gr is fixed to the minimum value Gr1. In this case, the heat pump heat quantity HPQ and the room temperature Tr increase slowly. For this reason, the room temperature Tr reaches the threshold temperature Rth at time t2.

  According to this embodiment, since the cooling water WT is supplied to the radiator 43 at the initial stage of the heat pump operation, in other words, when the heat load is large, the heat of the cooling water circuit 40 is effectively used to assist the start of the heat pump operation. can do. In addition, when the thermal load is reduced, the flow rate of the cooling water WT flowing through the radiator 43 is reduced and the flow rate of the cooling water WT flowing through the bypass passage 44 is increased, so that the amount of heat stored in the cooling water circuit 40 can be increased. Thereby, the amount of heat for frost suppression and / or defrosting after the heat load is reduced can be stored.

  FIG. 13 shows a defrosting process S710 executed by the control device 100 after the operation of the vehicle is completed. The defrosting process S710 reduces frost adhering to the outdoor heat exchanger 16, that is, the heat exchanger 70 after the operation of the vehicle is completed, and desirably removes the frost completely. Thereby, a heat pump driving | operation can be started from a state with little frost at the time of the next operation start. That is, the rise of the heat pump operation in the next operation is prevented from being hindered due to frost attached to the heat exchanger 70 in the previous operation.

  In S711, it is determined whether or not the operation of the vehicle has ended. Here, it can be determined whether or not the power switch of the vehicle or the ignition switch has been operated to the OFF position. When the operation of the vehicle ends, the process proceeds to S712. In S712, it is determined whether or not defrosting is necessary. For example, it is determined whether or not defrosting is necessary based on the duration of the heat pump operation during the previous operation, the outside air temperature, the temperature of the outdoor heat exchanger 16, the refrigerant temperature Te at the outlet of the outdoor heat exchanger 16, and the like. Can do. When defrosting is required, it progresses to S713. In S713, it is determined whether or not the amount of heat stored in the cooling water circuit 40 is at a level that can be used for defrosting. Here, it is determined whether or not the temperature Tw of the cooling water WT exceeds a predetermined threshold temperature Wth3. The plurality of threshold temperatures are set such that Wth3 <Wth1 <Wth2. The threshold temperature Wth3 is a temperature of 0 ° C. or higher. For example, the threshold temperature Wth3 is a temperature between 3 ° C. and 10 ° C. When the cooling water temperature Tw exceeds the threshold temperature Wth3 (Tw> Wth3), the process proceeds to S714. In S714, the thermal storage defrost (HOT-WT) using the heat stored in the cooling water circuit 40 is executed. Here, the pump 14 is operated (ON), the three-way valve 42 is switched to flow the cooling water WT to the radiator 43, and the fan 17 is stopped (OFF). Thereby, the heat pump cycle 2 is operated in the state of FIG.

  In this embodiment, the control device 100 absorbs heat from the outdoor heat exchanger 16 and changes the flow rate to the radiator 43 in accordance with the progress of the heat pump operation that supplies heat to the indoor condenser 12. , 42 are controlled. The cooling water WT supplied to the outdoor heat exchanger 16 supplies heat to the outdoor heat exchanger 16, and therefore pumps up heat, that is, promotes a heat pump. Moreover, the cooling water WT supplied to the outdoor heat exchanger 16 suppresses the adhesion of frost caused by the outdoor heat exchanger 16 directly or indirectly. When the flow rate is large, the effect of promoting the heat pump and the effect of suppressing frost formation are large. When the flow rate is small, heat is stored in the cooling water circuit 40. The heat stored in the cooling water circuit 40 can be used for promoting the heat pump, suppressing frost adhesion, or defrosting. According to this configuration, the flow rate of the cooling water WT supplied to the outdoor heat exchanger 16 is changed as the heat pump operation progresses. For this reason, promotion of a heat pump, suppression of frost formation, and the improvement of defrosting performance are achieved during the period of heat pump operation.

  In this embodiment, the control device 100 decreases the flow rate according to the progress of the heat pump operation. In other words, the control device 100 decreases the flow rate according to the decrease in the heat load of the heat pump operation. For example, when heat pump operation is used for heating, the flow rate is reduced as the room temperature increases. According to this configuration, the flow rate decreases as the heat load decreases. For this reason, the effect of promotion of a heat pump and suppression of adhesion of frost is exhibited largely in the initial stage of heat pump operation. Thereafter, heat storage in the auxiliary medium is performed, so that the defrosting performance is improved.

  In this embodiment, the control device 100 is a component of the cooling water circuit 40 so as to supply the cooling water WT to the radiator 43 in order to defrost the frost attached to the outdoor heat exchanger 16 after the heat pump operation is finished. To control. According to this structure, the frost adhering to the outdoor heat exchanger 16 is defrosted with the heat stored in the cooling water WT. And defrosting is performed after completion | finish of a heat pump driving | operation. Therefore, the influence of frost can be suppressed at the start of the next heat pump operation.

(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 said embodiment, the switching means which switches the refrigerant | coolant supplied to the heat exchanger 70 to a high pressure refrigerant | coolant and a low pressure refrigerant | coolant using the fixed throttle 13 and the on-off valve 15a was provided. Instead, in this embodiment, an expansion valve 213 is employed as shown in FIG. The expansion valve 213 is an electric expansion valve whose opening degree can be adjusted. The opening of the expansion valve 213 can be adjusted at least in a range from a small opening corresponding to the fixed throttle 13 to a large opening corresponding to the fully opened opening of the on-off valve 15a. The expansion valve 213 is controlled to a small opening that functions as a throttle during heating, and is controlled to a large opening during cooling.

(Third embodiment)
In the said embodiment, the defrost after operation completion was performed by thermal storage defrost (HOT-WT). In addition to this, in this embodiment, defrosting after operation is performed by hot gas defrosting (HOT-GAS) for supplying high-temperature refrigerant from the refrigerant circuit 10 to the outdoor heat exchanger 16. In this embodiment, when a sufficient amount of heat is not stored in the cooling water circuit 40, hot gas defrosting is executed instead of heat storage defrosting. According to the hot gas defrosting, the heat exchanger 70 can be defrosted without depending on the heat of the cooling water circuit 40.

(E) Hot gas defrosting operation (HOT-GAS)
The air conditioner 1 can execute the hot gas defrosting (HOT-GAS) illustrated in FIG. 15 in addition to the above embodiment. The control device 100 stops the circulation of the cooling water WT in the cooling water circuit 40 by stopping the pump 41. The refrigerant circuit 10 is operated so as to introduce the high-pressure refrigerant discharged from the compressor 11 directly into the outdoor heat exchanger 16. The on-off valve 15 a is driven to a fully open state so as to introduce high-pressure refrigerant directly into the outdoor heat exchanger 16. The refrigerant that has flowed out of the outdoor heat exchanger 16 is returned to the compressor 11 via the passage 20a. Furthermore, in order to suppress heat dissipation in the indoor condenser 12, the amount of air UR passing through the indoor condenser 12 is suppressed. In this embodiment, the control device 100 drives the air mix door 34 to a position where the passage to the indoor condenser 12 is closed.

  Alternatively or additionally, the fan 32 may be stopped. Further, a hot gas passage for directly introducing the high-pressure refrigerant discharged from the compressor 11 into the outdoor heat exchanger 16 may be provided. Further, the refrigerant discharged from the outdoor heat exchanger 16 may be supplied to the compressor 11 via the indoor evaporator 20.

  FIG. 16 shows a defrosting process S730 executed by the control device 100 after the operation of the vehicle is completed. The same reference numerals are assigned to the same processes as the defrosting process S710 described above. If it determines with the heat storage amount of the cooling water circuit 40 being insufficient in S713, it will progress to S731. In S731, hot gas defrosting (HOT-GAS) is performed. In S731, the pump 41 is stopped (OFF), and the compressor 11 is operated (ON). As a result, in this embodiment, when the cooling water circuit 40 cannot perform sufficient defrosting, hot gas defrosting is performed.

  This embodiment includes a hot gas device that introduces a high-pressure refrigerant into the outdoor heat exchanger 16. The hot gas equipment is provided by the passage 14 and the on-off valve 15a. The hot gas equipment may be provided by an expansion valve 213 or a hot gas passage. The control device 100 controls the hot gas equipment so that the high-pressure refrigerant is introduced into the outdoor heat exchanger 16 when the cooling water WT alone cannot be defrosted. According to this configuration, the high-pressure refrigerant is introduced into the outdoor heat exchanger 16 when defrosting cannot be performed only with the cooling water WT. For this reason, defrosting is possible without depending only on the heat storage to the cooling water WT.

(Fourth embodiment)
In the above embodiment, the three-way valve 42 that selects the radiator 43 or the bypass passage 44 is employed. Instead, in this embodiment, a configuration is adopted in which the ratio of the flow rate of the cooling water WT passing through the radiator 43 and the flow rate of the cooling water WT passing through the bypass passage 44 can be adjusted continuously or in multiple stages. Is done. According to this embodiment, in addition to the above-described embodiment, a combined heating operation (HEAT3) that uses heat storage and waste heat recovery in combination is provided.

(F) Combined heating operation (HEAT3)
In FIG. 17, the flow path of the three-way valve 442 can be configured to pass through both the radiator 43 and the bypass passage 44. Further, a flow rate adjusting valve 45 is provided in the bypass passage 44. The flow rate adjusting valve 45 adjusts the ratio of the flow rate passing through the radiator 43 and the flow rate passing through the bypass passage 44. The flow rate adjusting valve 45 provides a valve device for the flow rate regulator. The cooling water WT flowing in the radiator 43 conveys the heat obtained in the heat exchanger 80 to the heat exchanger 70. The cooling water WT flowing through the bypass passage 44 stores heat supplied from the external heat source HS in the cooling water circuit 40. In the combined heating operation (HEAT3), frost adhesion and growth on the outdoor heat exchanger 16 and the heat exchanger 70 are suppressed while supplementing the heating capacity by supplying the heat of the external heat source HS to the refrigerant circuit 10. To do. Further, in the combined heating operation (HEAT3), heat storage for the defrosting operation proceeds simultaneously.

  In FIG. 18, the control device 100 adjusts the flow rate of the cooling water WT to the radiator 43 according to the heat load of the air conditioner 1 that is a heat utilization device in the heating operation. The control device 100 controls the flow rate adjustment valve 45 so that the flow rate of the cooling water WT flowing through the radiator 43 decreases continuously or stepwise as the heat load increases. Specifically, the control device 100 increases the opening degree of the flow control valve 45 as the heat load increases. Therefore, the opening degree of the flow control valve 45 is controlled to gradually decrease in the process in which the heat pump operation proceeds and the thermal load gradually decreases. As a result, the flow rate of the cooling water WT flowing through the radiator 43 gradually increases. In this embodiment, the flow rate to the radiator 43 is adjusted based on the refrigerant temperature Te at the outlet of the outdoor heat exchanger 16 without directly detecting the heat load. The refrigerant temperature Te decreases as the heat pump operation continues and frost formation on the outdoor heat exchanger 16 proceeds. For this reason, the refrigerant temperature Te exhibits a behavior close to a decrease in heat load due to the continuation of the heat pump operation.

  Instead of the refrigerant temperature Te, the refrigerant pressure in the outdoor heat exchanger 16 or at the outlet of the outdoor heat exchanger 16 may be used. The refrigerant pressure also decreases as frost formation on the outdoor heat exchanger 16 proceeds.

  The control device 100 executes a control process S640 for controlling the cooling water circuit 40. In S641, the opening degree DV of the flow rate adjustment valve 45 is set based on the refrigerant temperature Te at the outlet of the outdoor heat exchanger 16, and the flow rate adjustment valve 45 is controlled so as to be the opening degree. The refrigerant circuit 10 is controlled such that the room temperature TR approaches and is maintained at a predetermined threshold temperature Rth. For example, the control device 100 feedback-controls the rotation speed of the compressor 11 based on a proportional component that depends on the difference between the room temperature TR and the threshold temperature Rth. The refrigerant in the outdoor heat exchanger 16 absorbs heat necessary for controlling the room temperature TR to the threshold temperature Rth. When the outdoor heat exchanger 16 can sufficiently absorb heat, the refrigerant temperature Te is stabilized at a relatively high temperature. However, when the amount of frost on the outdoor heat exchanger 16 increases, the refrigerant temperature Te decreases. Therefore, in the initial stage of the heat pump operation, the refrigerant temperature Te takes a high value, but after the heat pump operation is continued to the extent that frosting occurs, the refrigerant temperature Te takes a low value. Therefore, by setting the opening degree DV based on the refrigerant temperature Te, the opening degree DV corresponding to the progress of the heat pump operation, that is, the flow rate of the radiator 43 can be set.

  The function f (Te) for setting the opening degree DV based on the refrigerant temperature Te can be given as, for example, a combined function of the function f1 and the function f2 illustrated in S641. The function f1 sets the flow rate Gr of the cooling water WT flowing through the radiator 43 according to the refrigerant temperature Te. The function f1 can be set so as to change according to the outside air temperature Tam. For example, the function f1 can be set so that the flow rate Gr decreases as the refrigerant temperature Te increases. The function f1 can be set so that the flow rate Gr increases as the outside air temperature Tam decreases. The plurality of functions f1 shown in the figure can be set for each representative outside air temperature in a region where the outside air temperature Tam is 0 ° C. or less.

  The function f2 sets the opening degree DV according to the flow rate Gr. The function f2 is set to decrease the opening degree DV as the flow rate Gr increases. The function f2 can be set to reflect the viscosity of the cooling water WT. For example, the function f2 can be set to change according to the outside air temperature Tam that affects the viscosity. The plurality of functions f2 shown in the figure can be set for each representative outside air temperature in a region where the outside air temperature Tam is 0 ° C. or less. In order to correct the functions f, f1, and f2, the cooling water temperature Tw may be used instead of the outside air temperature Tam.

  According to this embodiment, a part of the total flow rate of the cooling water circuit 40 flows into the radiator 43 to assist the pumping of heat by the refrigerant circuit 10, and the remainder flows into the bypass passage 44 to the cooling water circuit 40. Run the heat storage.

  FIG. 19 shows changes in the heat pump heat quantity HPQ, the room temperature Tr, the refrigerant temperature Te at the outlet of the outdoor heat exchanger 16 and the flow rate Gr of the cooling water WT passing through the radiator 43 after the heat pump operation is started. In the figure, the solid line indicates this embodiment EMB4. The broken line indicates the comparative example CMP. The heat pump operation is started at time t0. At this time, the room temperature Tr is lower than the threshold temperature Rth. Therefore, the control device 100 operates the refrigerant circuit 10 so that the room temperature Tr approaches the threshold temperature Rth, and further, the room temperature Tr is maintained at the threshold temperature Rth. The control device 100 adjusts the flow rate Gr to the minimum value Gr1. The refrigerant circuit 10 absorbs heat from the air AR and the cooling water WT and raises the room temperature. After time t0, the heat pump heat quantity HPQ rises rapidly. Correspondingly, the room temperature Tr also rises rapidly. As the room temperature Tr approaches the threshold temperature Rth, the heat pump heat quantity HPQ gradually decreases. After the refrigerant temperature Te rapidly decreases to the evaporation temperature, it gradually decreases as the amount of frost attached to the outdoor heat exchanger 16 and the heat exchanger 70 increases. As the refrigerant temperature Te decreases, the flow rate Gr gradually increases from the minimum value Gr1.

  When the room temperature Tr reaches the threshold temperature Rth at time t1, the refrigerant flow rate decreases and the refrigerant temperature Te slightly increases. The heat pump operation is continued even after time t1. The refrigerant circuit 10 absorbs heat from the air AR and the cooling water WT. For this reason, the amount of frost attached to the outdoor heat exchanger 16 and the heat exchanger 70 gradually increases. Therefore, the refrigerant temperature Te gradually decreases. Therefore, the flow rate Gr gradually increases toward the maximum value Gr2.

  According to this embodiment, since a part of the cooling water WT is supplied to the radiator 43 at the initial stage of the heat pump operation, in other words, when the heat load is large, the heat pump operation is performed by effectively using the heat of the cooling water circuit 40. Can be helped. When the heat pump operation continues and the heat pump operation time becomes longer, frost may adhere to the outdoor heat exchanger 16 and the heat exchanger 70 and gradually grow. In this embodiment, when the heat pump operation time becomes longer and the thermal load becomes smaller, the flow rate Gr of the cooling water WT flowing through the radiator 43 is increased. For this reason, adhesion of frost during heat pump operation and growth of frost can be suppressed. On the other hand, since the cooling water WT is also passed through the bypass passage 44, the amount of heat stored in the cooling water circuit 40 can be increased. Thereby, the calorie | heat amount for a defrost after the operation | movement of a vehicle is complete | finished can be stored.

  In this embodiment, the control device 100 increases the flow rate according to the progress of the heat pump operation. In other words, the control device 100 increases the flow rate according to an increase in the amount of frost on the outdoor heat exchanger 16. Specifically, the control device 100 increases the flow rate according to a decrease in the refrigerant temperature Te or the refrigerant pressure of the outdoor heat exchanger 16. According to this configuration, the flow rate increases as the amount of frost formation increases. For this reason, heat storage to the auxiliary medium is performed at the initial stage of the heat pump operation. Thereafter, the effects of promoting the heat pump and suppressing the adhesion of frost are greatly exhibited. For example, the amount of frost formation can be known from the temperature or pressure of the refrigerant at the outlet of the endothermic heat exchanger. Since the refrigerant temperature or the refrigerant pressure decreases with an increase in the amount of frost formation, the flow rate can be increased with a decrease in the refrigerant temperature or the refrigerant pressure.

(Fifth embodiment)
In the said embodiment, thermal storage defrost (HOT-WT) and hot gas defrost (HOT-GAS) were selectively performed. Instead, in this embodiment, a combined defrosting operation (HOT-WT & HOT-GAS) using both heat storage defrosting and hot gas defrosting is provided.

(G) Combined defrosting operation (HOT-WT & HOT-GAS)
In FIG. 20, the control device 100 controls the cooling water circuit 40 so as to provide the heat storage defrost. At the same time, the control device 100 controls the refrigerant circuit 10 so as to provide hot gas defrosting.

  FIG. 21 shows the defrosting process S750 executed by the control device 100 after the operation of the vehicle is finished. In S751, it is determined whether the heat storage amount satisfies a predetermined condition. Here, it is determined whether or not the cooling water temperature Tw is lower than a predetermined threshold temperature Wth3 and the cooling water temperature Tw is higher than the outside air temperature Ta. If the condition is satisfied (Tam <Tw <Wth3), the process proceeds to S752. Since the cooling water temperature Tw is lower than the threshold temperature Wth3, it is considered that defrosting using only the cooling water WT is difficult. However, it is considered that the frost can be heated because the cooling water temperature Tw is higher than the outside air temperature Tam. That is, sufficient defrosting is difficult only by heat storage defrosting. In S752, combined defrost (HOT-WT & HOT-GAS) is executed. If the above condition is not satisfied, the process proceeds to S731.

  In this embodiment, hot gas defrosting is performed when sufficient defrosting cannot be performed only by heat storage defrosting. In addition, when the cooling water WT can be used as a heat source higher than the outside air temperature Tam, the heat storage defrost is executed in addition to the hot gas defrost. As a result, the heat left in the cooling water WT can be used effectively.

(Sixth embodiment)
In the above embodiment, two defrosting operations were selectively executed. Instead, in this embodiment, heat storage defrost, hot gas defrost, and combined defrost are selectively executed. The plurality of defrosting operations are selected according to the amount of heat stored in the cooling water circuit 40. The plurality of defrosting operations are controlled such that hot gas defrosting is additionally or alternatively performed when sufficient defrosting is not possible by heat storage defrosting alone.

  FIG. 22 shows a defrosting process S760 executed by the control device 100 after the operation of the vehicle is completed. When the cooling water temperature Tw does not exceed the threshold temperature Wth3 in S713, the process proceeds to S751. In this embodiment, when the amount of stored heat is sufficiently large, heat storage defrosting is performed. Hot gas defrosting is performed when sufficient defrosting cannot be performed only by heat storage defrosting. In addition, when the cooling water WT can be used as a heat source higher than the outside air temperature Tam, the heat storage defrost is executed in addition to the hot gas defrost. As a result, the heat left in the cooling water WT can be used effectively.

(Seventh embodiment)
In this embodiment, in addition to the above-described embodiment, when the heat storage amount is small and the cooling water WT cannot contribute to defrosting at all, the cooling water circuit 40 is not defrosted only by the refrigerant circuit 10 without performing the heat storage defrosting operation. To do.

  FIG. 23 shows the defrosting process S770 executed by the control device 100 after the operation of the vehicle is completed. When the cooling water temperature Tw does not exceed the first threshold temperature Wth3 in S713, the process proceeds to S771. In S771, it is determined whether or not the cooling water temperature Tw exceeds a predetermined second threshold temperature Wth4. The threshold temperature Wth4 is a temperature lower than the threshold temperature Wth3. Therefore, the plurality of threshold temperatures are set to satisfy Wth4 <Wth3 <Wth1 <Wth2. The threshold temperature Wth4 is a threshold for determining whether or not the cooling water WT can contribute to defrosting even a little. For example, the threshold temperature Wth4 can be set to 0 ° C. When the cooling water temperature Tw exceeds the threshold temperature Wth4 (Tw> Wth4), the process proceeds to S751. When the cooling water temperature Tw does not exceed the threshold temperature Wth4 (Tw = <Wth4), the process proceeds to S731.

  In this embodiment, when the amount of stored heat is sufficiently large, heat storage defrosting is performed. Hot gas defrosting is performed when sufficient defrosting cannot be performed only by heat storage defrosting. In addition, when the cooling water WT can be used as a heat source higher than the outside air temperature Tam, the heat storage defrost is executed in addition to the hot gas defrost. However, when the cooling water WT cannot contribute to defrosting, only hot gas defrosting is performed.

(Eighth embodiment)
In the above embodiment, the fan 17 is stopped when the defrosting operation is performed. Instead, in this embodiment, when the outside air temperature Tam can contribute to defrosting, the fan 17 is operated and the amount of heat of the outside air is used to promote defrosting.

  FIG. 24 shows the defrosting process S780 executed by the control device 100 after the operation of the vehicle is completed. In the figure, the above-described S713, S771, and S751 are shown as single steps for determining the heat storage amount based on the cooling water temperature Tw. In S781, it is determined whether or not the outside air temperature Tam can contribute to defrosting. When the outside air temperature Tam exceeds the predetermined threshold temperature Ath (Tam> Ath), the process proceeds to S782. In S <b> 782, the fan 17 is operated (ON) to supply outside air to the heat exchanger 70. Thereby, the heat of outside air contributes to raising the temperature of frost.

  If the outside air temperature Tam does not exceed the threshold temperature Ath (Tam = <Ath), the process proceeds to S783. In S783, the fan 17 is stopped (OFF). Thereby, it is avoided that defrosting is prevented by low temperature outside air.

  As the threshold temperature Ath, a fixed value or a variable value can be used. For example, the threshold temperature Ath can be the temperature of the outdoor heat exchanger 16 or the heat exchanger 70 or a refrigerant temperature indicating the temperature. For example, the refrigerant temperature Te at the outlet of the outdoor heat exchanger 16 represents the surface temperature of the outdoor heat exchanger 16. Therefore, the refrigerant temperature Te may be used as the threshold temperature Ath.

  According to this embodiment, in addition to heat storage defrosting or hot gas defrosting, the heat of the outside air can be effectively used for defrosting.

(Ninth embodiment)
In the above embodiment, the cooling water circuit 40 includes the single external heat source HS. Instead, this embodiment includes a plurality of external heat sources. In this embodiment, as shown in FIG. 25, the cooling water circuit 40 is configured such that the battery BT and the cooling water WT can exchange heat. The battery BT and the cooling water WT are thermally coupled directly or indirectly through the temperature control device of the battery BT. For example, the battery BT and the piping of the cooling water WT can be brought into direct contact. Moreover, you may provide the heat exchanger which heat-exchanges the air of the storage space of the battery BT, and the cooling water WT. The battery BT is provided in parallel with a closed circuit including the external heat source HS and the radiator 43. On the closed circuit, in parallel with the battery BT, a flow rate adjustment valve 46 for flowing the cooling water WT to the battery BT is provided. A temperature sensor 54 that detects a surface temperature representative of the temperature of the battery BT or a cooling water temperature is provided on the surface of the battery BT or a cooling water passage downstream of the battery BT. The temperature detected by the temperature sensor 54 is called the battery temperature Tb.

  The external heat source HS provides a main external heat source. The battery BT also provides an auxiliary external heat source. Cooling water WT takes heat from battery BT and is used to cool battery BT. Cooling water WT is also used to heat battery BT and heat battery BT. According to this configuration, the waste heat of the battery BT can be supplied to the cooling water. As a result, the waste heat of the battery BT can be used for suppressing frost formation and / or defrosting.

  FIG. 26 shows a defrosting process S790 executed by the control device 100 after the operation of the vehicle is completed. If heat storage defrost is performed in S714, it will progress to S791. In S791, it is determined whether the heat of the battery BT can be further used during the heat storage defrosting. Here, after the operation of the vehicle is finished, the determination as to whether or not the battery BT is charged by an external power source can be used. When the battery BT is charged by an external power source, the battery BT generates heat, so that the heat of charging can be used for defrosting. Moreover, you may utilize determination of whether battery temperature Tb exceeds predetermined threshold temperature Bth. For example, when the battery temperature Tb exceeds the threshold temperature Bth, it can be determined that the heat of the battery BT can be used for defrosting. When the heat of the battery BT can be used for defrosting, the process proceeds to S792.

  For example, S791 can be configured to proceed to S792 while the battery BT is being charged. Further, S791 may be configured to proceed to S792 after the charging of the battery BT is completed. Further, S791 may be configured to proceed to S792 from when the battery BT is being charged until after the charging is completed. According to these configurations, waste heat during charging can be used for defrosting.

  In S792, the heat of the battery BT is used. In S792, by closing the flow rate adjustment valve 46, the cooling water WT is supplied to the battery BT, the heat of the battery BT is taken out to the cooling water circuit 40, and the heat is supplied to the radiator 43.

  The cooling water temperature Tw can be used as the threshold temperature Bth. For example, in S791, it may be determined whether or not the battery temperature Tb exceeds the cooling water temperature Tw. When the battery temperature Tb exceeds the cooling water temperature Tw (Tb> Tw), heat storage defrosting using the heat of the battery BT is performed. Further, when the battery temperature Tb does not exceed the cooling water temperature Tw (Tb = <Tw), heat storage defrosting using heat of the external heat source HS is executed.

(10th Embodiment)
Instead of the above embodiment, the battery BT may be provided as shown in FIG. Also in this configuration, the flow rate of the cooling water WT flowing through the battery BT can be adjusted by the flow rate adjustment valve 46.

(Eleventh embodiment)
Instead of the above embodiment, the battery BT may be provided as shown in FIG. The battery BT is provided in a bypass passage in parallel with the external heat source HS. The flow rate adjusting valve 46 is provided in the bypass passage so as to be positioned in series with the battery BT.

(Twelfth embodiment)
Instead of the above embodiment, the battery BT may be provided as shown in FIG. Also in this configuration, the flow rate of the cooling water WT flowing through the battery BT can be adjusted by the flow rate adjustment valve 46.

(13th Embodiment)
Instead of the above embodiment, the battery BT may be provided as shown in FIG. The battery BT is provided in parallel with a closed circuit including the external heat source HS and the radiator 43. In this embodiment, a flow rate adjustment valve 46 in parallel with the battery BT and a flow rate adjustment valve 47 in series with the battery BT are provided.

(14th Embodiment)
Instead of the above embodiment, the battery BT may be provided as shown in FIG. In this embodiment, a flow rate adjustment valve 46 is provided in parallel with the battery BT, and a flow rate adjustment valve 47 is provided in the bypass passage 44. According to this configuration, the cooling water WT flows into the bypass passage 44 by opening the flow rate adjustment valve 47. The cooling water WT flows into the radiator 43 by closing the flow rate adjusting valve 47 and opening the flow rate adjusting valve 46. Further, the flow rate adjusting valve 47 is closed and the flow rate adjusting valve 46 is closed, whereby the cooling water WT flows through the battery BT and the radiator 43.

(Fifteenth embodiment)
Instead of the above embodiment, the battery BT may be provided as shown in FIG. Also in this configuration, the flow rate of the cooling water WT flowing through the battery BT can be adjusted by the flow rate adjustment valve 46.

(Sixteenth embodiment)
In addition to the above embodiment, as shown in FIG. 33, the cooling water circuit 40 may be provided with a heater core 48 for heating the air UR. The heater core 48 is disposed on the upstream side of the radiator 43. The cooling water circuit 40 is provided with a flow rate adjustment valve 49 in parallel with the heater core 48. The control device 100 controls the flow rate adjustment valve 49 to supply the cooling water WT to the heater core 48 when the cooling water temperature Tw exceeds a predetermined threshold temperature. As a result, the heat of the cooling water WT can be directly used for air conditioning. Furthermore, since the cooling water WT after passing through the heater core 48 is supplied to the radiator 43, the amount of heat supplied to the radiator 43 can be adjusted. For example, when the amount of heat generated by the external heat source HS is large, the amount of heat given to the radiator 43 can be adjusted to an appropriate amount by heat radiation from the heater core 48.

(17th Embodiment)
In addition to the above embodiment, as shown in FIG. 34, a heater core 48 may be provided in parallel with the external heat source HS. In other words, the cooling water circuit 40 includes a heater core 48 provided in a passage that bypasses the radiator 43. In order to dissipate excessive heat from the heater core 48, the control device 100 controls the cooling water circuit 40 so that the cooling water WT flows through the heater core 48 when the amount of heat supplied from the external heat source HS is large. Even in this configuration, the excessive heat stored in the cooling water circuit 40 can be used in the heater core 48.

(Eighteenth embodiment)
In the above embodiment, as illustrated in FIG. 11, in the heating operation, the control device 100 executes the waste heat recovery operation HEAT2 when the heat load of the air conditioner 1 exceeds a predetermined value, and the heat load reaches a predetermined value. When it falls below, normal heating operation HEAT1 was executed. Instead, this embodiment provides continuous or multi-step control over both normal heating and waste heat recovery operations.

  As illustrated in FIG. 35, the control device 100 executes a control process 680 for controlling the cooling water circuit 40. The same steps as those described above are denoted by the same reference numerals. In S611, it is determined whether the heat pump operation HP is in an ON state, that is, whether it is being executed. When the heat pump operation HP is being executed, the process proceeds to S681. In S681, it is determined whether rapid heating is necessary. In S681, it is determined whether it is in the rapid heating state or the stable heating state. For example, it can be determined that the rapid heating state is in a period in which the air conditioner 1 is immediately after startup and the room temperature Tr has not yet reached the target temperature Tset. Thereafter, after the room temperature Tr reaches the target temperature Tset, it can be determined that the room is in the stable heating state.

  It may replace with this and may determine with it being in a rapid heating state for the predetermined time (t0-t1) after the air conditioner 1 was started. After a predetermined time (t0-t1) has elapsed after the air conditioner 1 is activated, it can be determined that the air conditioner 1 is in a stable heating state.

  When rapid heating is affirmed in S681, the process proceeds to S682. S682 provides a feedforward control unit that controls the flow rate of the cooling water WT supplied from the cooling water circuit 40 to the radiator 43 in a predictive or feedforward manner. In S682, the flow rate supplied to the radiator 43 by the pump 41 and the three-way valve 42 is adjusted to the maximum flow rate Gr2. Therefore, the heat pump cycle 2 becomes the waste heat recovery operation HEAT2. Supply of heat from the cooling water circuit 40 to the heat exchanger 70 compensates for a lack of heating capacity. In particular, the heat of the cooling water circuit 40 is used for heating in the winter when the temperature of the air AR is low. Moreover, the power consumption of the compressor 11 for providing the heat pump operation HP is suppressed. Furthermore, the growth of frost in the heat exchanger 70 is suppressed by causing the cooling water WT to flow through the water tube 43a.

  When rapid heating is denied in S681, the process proceeds to S613. S613 and S683-S686 provide a feedback control unit that controls the flow rate of the cooling water WT supplied from the cooling water circuit 40 to the radiator 43 in response to a feedback element. The feedback control unit increases the flow rate from the base value in response to a plurality of feedback elements using the limited flow rate Grs for storing heat in the cooling water circuit 40 as a base value. The feedback element may include external heat source information for maintaining the temperature of the external heat source HS at a predetermined value. For example, when the temperature of the external heat source HS is excessive, the flow rate is increased. The feedback element can include information for defrosting in the heat exchanger 70. For example, when defrosting is required, the flow rate is increased. The feedback element can include information indicating an excess or deficiency of capacity for heat pump operation. For example, if the heat pump capacity is insufficient, the flow rate is increased.

  In S613, the flow rate is adjusted so as to control the temperature of the external heat source HS. For details of S613, refer to the preceding description. S613 provides means for increasing the flow rate Gr of the cooling water WT when the cooling water temperature Tw exceeds the predetermined determination values Wth1 and Wth2. S613 is also processing for determining whether or not the amount of heat stored in the coolant circuit 40 is excessive. When the heat storage amount is excessive, the process proceeds to S686 described later. When the heat storage amount is within the appropriate range, the process proceeds to S683.

  The control device 100 increases the flow rate Gr when the temperature (Tw) of the auxiliary medium is higher than the predetermined temperature (Wth1, Wth2) than the flow rate when the temperature (Tw) of the auxiliary medium is lower than the predetermined temperature (Wth1, Wth2). (+ Grfb). This increase amount can be configured to be given after reaching the boundary between rapid heating and stable heating. According to this configuration, the temperature of the auxiliary medium is controlled so that the temperature of the heat source is controlled to a temperature corresponding to the predetermined temperature.

  In S683, it is determined whether or not defrosting is necessary. When defrosting is required, it progresses to S686. When defrosting is unnecessary, it progresses to S684. When a plurality of conditions are satisfied, the necessity for defrosting can be positively determined. It can be one of the conditions that the temperature of the heat exchanger 70 is low enough to cause frost. One of the conditions can be that the cooling water temperature Tw is relatively high enough to defrost, that is, exceeds a predetermined defrost determination value. It can be one of the conditions that the vehicle is in a state where defrosting can be performed. It can be one of the conditions that the traveling speed of the vehicle is below a predetermined determination value. One of the conditions can be that the vehicle is not operated, for example, that a power switch such as an ignition switch is in the off position.

  The control device 100 increases the flow rate Gr after determining that the endothermic heat exchanger 16 needs to be defrosted over the flow rate Gr before determining that the endothermic heat exchanger 16 needs to be defrosted (+ Grfb). ). This increase amount can be configured to be given after reaching the boundary between rapid heating and stable heating. According to this configuration, the flow rate is increased so as to defrost the endothermic heat exchanger 16.

  In S684, it is determined whether the heat pump capability of the refrigerant circuit 10 is insufficient. In other words, in S684, it is determined whether the heat pump capability is sufficient. When the refrigerant circuit 10 cannot exhibit the heat pump capability that can maintain the target temperature Tset, an affirmative determination can be made. For example, when the room temperature Tr falls below a predetermined threshold Tp that is lower than the target temperature Tset, an affirmative determination can be made as to the lack of heat pump capacity. When the room temperature Tr does not fall below the threshold value Tp, a negative determination can be made as to the lack of heat pump capability.

  Alternatively, the lack of heat pump capability may be determined based on the duration of heat pump operation. As the duration time of the heat pump operation becomes longer, the amount of frost formation on the heat exchanger 70 increases, and the heat pump capacity decreases proportionally. During a predetermined time (t0-t3) after the heat pump operation of the refrigerant circuit 10 is started, it can be determined that the heat pump capacity is insufficient. After a predetermined time (t0-t3) has elapsed after the start of the heat pump operation, an affirmative determination can be made that the heat pump capacity is insufficient.

  Further, instead of the above, the lack of heat pump capacity may be determined based on the temperature at which the indoor condenser 12 is blown. When the blowing temperature of the indoor condenser 12 exceeds the necessary blowing temperature TAO, a negative determination can be made as to the lack of heat pump capacity. If the blowing temperature of the indoor condenser 12 does not exceed the necessary blowing temperature TAO, an affirmative determination can be made that the heat pump capacity is insufficient.

  The control device 100 gradually increases the flow rate Gr (+ Grfb) in response to a temperature (Tp, TAO) or time (t0-t3) indicating an increase in the amount of frost on the endothermic heat exchanger 16. This increase amount can be configured to be given after reaching the boundary between rapid heating and stable heating. According to this structure, the capability shortage by the increase in the amount of frost formation of the endothermic heat exchanger 16 can be suppressed.

  In S685, the flow rate supplied to the radiator 43 by the pump 41 and the three-way valve 42 is adjusted to the limit flow rate Grs. In S685, the flow rate is adjusted stepwise or gradually. For example, when the flow reaches S685 after passing through S682, the flow rate is gradually decreased from the maximum flow rate Gr2 to the limit flow rate Grs. The limited flow rate Grs is a flow rate at which the waste heat of the external heat source HS can be stored in the cooling water circuit 40. The limit flow rate Grs can be the minimum flow rate Gr1. The limit flow rate Grs can be a predetermined value between the minimum flow rate Gr1 and the maximum flow rate Gr2.

  The control device 100 increases the flow rate before reaching the boundary between rapid heating and stable heating indicated by the temperature (Rth, Tset) or time (t0-t1) of the air UR heated by the use side heat exchanger 12 ( Gr2) is supplied. Further, after reaching the boundary, a limited flow rate (Grs, Gr1) smaller than the large flow rate is supplied. According to this structure, promotion of a heat pump and suppression of frost adhesion are achieved in rapid heating. Thereafter, heat is stored in the auxiliary medium in stable heating.

  In S686, the flow rate supplied to the radiator 43 by the pump 41 and the three-way valve 42 is increased by the increase amount Grfb. In S686, the flow rate is adjusted stepwise or gradually. For example, when the flow reaches S686 after passing through S685, the flow rate is gradually increased from the limit flow rate Grs by the increase amount Grfb.

  The increase amount Grfb can be set continuously or stepwise depending on the feedback factor. The increase amount Grfb can be set in proportion to the temperature of the external heat source HS or the heat storage amount of the cooling water circuit 40. The increase amount Grfb can be set proportionally according to the necessity of defrosting. The increase amount Grfb can be set proportionally according to the insufficient amount of heat pump capacity. The increase amount Grfb may be gradually increased in proportion to the duration of the heat pump operation.

  FIG. 36 shows an example of the progress of the heat pump operation. The progress of the heat pump operation can be shown by the change in the room temperature Tr. The progress of the heat pump operation extends over a period in which the room temperature Tr rises toward the target temperature Tset and a period in which the room temperature Tr is maintained near the target temperature Tset. In the figure, a broken line QP indicates a heat pump heat amount that the refrigerant circuit 10 can exhibit, that is, a potential amount QP. The solid line QU indicates the heat pump heat quantity that the refrigerant circuit 10 actually uses in order to achieve the target temperature Tset, that is, the used quantity QU. A one-dot chain line QS shows an example in which the potential amount QP continues to decrease. A solid line Gr (EMB) indicates a waveform in this embodiment. A broken line Gr (MOD) indicates a waveform according to the modification.

  At time t0, the heat pump operation of the refrigerant circuit 10 is started. The room temperature Tr at time t0 is sufficiently lower than the target temperature Tset. Therefore, the necessity for rapid heating is affirmed. After time t0, control called rapid heating or warm-up is provided by S611, S681, and S682.

  The potential amount QP increases rapidly after time t0. Between the time t0 and the time t1, the potential amount QP exceeds the usage amount QU. This is because the maximum flow rate Gr2 is supplied during this period and the amount of frost formation is small. In a process in which the room temperature Tr approaches the target temperature Tset after the time t0, the usage amount QU gradually decreases. At this time, frost gradually adheres to the heat exchanger 70. The potential amount QP gradually decreases mainly due to an increase in the amount of frost formation.

  At time t1, the room temperature Tr reaches the target temperature Tset (Tr = Tset). At time t1, the necessity for rapid heating is negatively determined. After time t1, control called stable heating is provided by S611, S681, S613, and S683-S686. After the time t1, the flow rate Gr of the cooling water WT is gradually decreased from the maximum flow rate Gr2 to the limit flow rate Grs, and therefore the potential amount QP gradually decreases. After time t1, the amount of frost on the heat exchanger 70 gradually increases. As a result, the potential amount QP continues to decrease slowly. In this stable heating, the room temperature Tr is maintained at the target temperature Tset by gradually increasing the power consumption of the compressor 11.

  The target temperature Tset is used as a threshold for determining the end of rapid heating. The time (t0-t1) between the time t0 and the time t1 is a predetermined time that defines the rapid heating period. Therefore, the flow rate Gr of the cooling water WT supplied to the heat exchanger 70 is decreased in the process in which the room temperature Tr reaches the threshold value Tset, or in the process in which the rapid heating continues for a predetermined time. As indicated by the broken line Gr (MOD), the flow rate Gr may be decreased gradually or stepwise before and after the room temperature Tr reaches the threshold value Tset, or before and after the rapid heating duration reaches a predetermined time.

  As shown in the figure, the flow rate Gr is adjusted to the large flow rate Gr2 at least temporarily during the rapid heating period. The flow rate Gr is adjusted to a limited flow rate Grs that is less than the large flow rate Gr2 at least temporarily within the period of stable heating. The flow rate Gr is decreased in a period including the boundary between rapid heating and stable heating, that is, before and after the time t1. The reduction of the flow rate Gr can be performed gradually or stepwise as shown in the figure.

  At time t2, the potential amount QP is less than the usage amount QU. As a result, after time t2, the heat pump capability is insufficient. If the heat pump capability is insufficient, the room temperature Tr is not maintained at the target temperature Tset. As a result, the room temperature Tr gradually decreases.

  At time t3, the room temperature Tr falls below the threshold value Tp. After time t3, the flow rate Gr of the cooling water WT supplied to the heat exchanger 70 is increased by S684 and S686. As a result, an excessive decrease in the potential amount QP as indicated by the one-dot chain line QS is avoided. After time t3, the potential amount QP and the usage amount QU increase, and the room temperature Tr increases toward the target temperature Tset.

  After the time t3, the flow rate Gr is gradually increased from the limit flow rate Grs, so that the potential amount QP gradually increases. The threshold value Tp is used as a threshold value for determining the lack of heat pump capacity. The time between time t0 and time t3 (t0-t3) is a predetermined time that defines the duration of heat pump operation that is expected to cause a shortage of heat pump capacity. Therefore, the flow rate Gr of the cooling water WT supplied to the heat exchanger 70 is increased in the process in which the room temperature Tr reaches the threshold value Tp or in the process in which the duration of the heat pump operation reaches a predetermined time. The flow rate Gr may be increased before and after the room temperature Tr reaches the threshold value Tp, or before and after the duration of the heat pump operation reaches a predetermined time.

  As illustrated, the flow rate Gr is adjusted to the limited flow rate Grs at least temporarily within the period of stable heating. The flow rate Gr is increased at least temporarily by the increase amount Grfb during the stable heating period. The flow rate Gr is increased in a boundary including a shortage of heat pump capability, that is, a period including before and after time t3. This increase in the flow rate Gr can be performed gradually or stepwise as shown.

  According to this embodiment, the cooling water WT having a large flow rate Gr2 is supplied to the heat exchanger 70 in the initial stage of the heat pump operation. Therefore, the heat pump capability can be supplemented by the cooling water WT. In particular, the heating capacity at low temperatures is supplemented. Further, excessive power consumption by the compressor 11 is suppressed. Moreover, the frost on the heat exchanger 70 can be suppressed.

  According to this embodiment, after the start of the heat pump operation, before and after the room temperature Tr reaches the target temperature Tset, the flow rate Gr is decreased toward the limited flow rate Grs that is smaller than the large flow rate Gr2. Therefore, the heat of the external heat source HS is stored in the coolant circuit 40. Eventually, when the amount of stored heat becomes excessive, the flow rate Gr is increased. As a result, the heat storage amount is feedback controlled within an appropriate range. Further, when the heat exchanger 70 needs to be defrosted, the flow rate Gr is increased. As a result, excessive frost formation on the heat exchanger 70 is suppressed. Further, when the heat pump capability is insufficient, the flow rate Gr is increased. As a result, the heat pump capability can be supplemented by the cooling water WT.

(Nineteenth embodiment)
In the said embodiment, in the heat exchanger 70, the several tubes 16a and 43a were arrange | positioned so that at least 1 water tube 43a may face the upstream of the flow direction of the air AR. In other words, the plurality of tubes 16a and 43a are arranged so that at least one, preferably the plurality of water tubes 43a, can be seen from the upstream surface of the heat exchanger 70 with respect to the flow of the air AR. In the illustrated form, when viewed from the upstream surface of the heat exchanger 70, the refrigerant tubes 16a and the water tubes 43a appear alternately. This configuration is advantageous in that the temperature of the high-temperature medium supplied to the water tube 43a is exerted on the most upstream portion in the flow direction of the air AR in the heat exchanger 70 to suppress the growth of frost.

  As illustrated in FIG. 37, in the configuration of FIG. 10 according to the first embodiment, the plurality of tubes 16a and 43a are provided at least in the upstream row with respect to the flow direction of the air AR, and the upstream row. It arrange | positions so that the downstream row | line | column located downstream may be comprised. Further, in the plurality of tubes 16a and 43a, the refrigerant tube 16a and the water tube 43a are disposed adjacent to each other in at least a part of the upstream row. Desirably, the plurality of refrigerant tubes 16a and the plurality of water tubes 43a are alternately arranged in the entire upstream row.

  From another viewpoint, at least one water tube 43a does not have the refrigerant tube 16a at a position overlapping the flow direction of the air AR upstream of the water tube 43a itself in the flow direction of the air AR. The plurality of tubes 16a and 43a are arranged. As shown in the drawing, the water tube 43a does not have the refrigerant tube 16a at a position overlapping with the flow direction of the air AR. And the water tube 43a is arrange | positioned so that the refrigerant | coolant tube 16a may be adjoined regarding the direction orthogonal to the flow direction of the air AR. The adjacent relationship between the refrigerant tube 16a and the water tube 43a in the orthogonal direction is provided by arranging the refrigerant tubes 16a on both sides of one water tube 43a. This arrangement relationship can be provided by arranging the plurality of refrigerant tubes 16a and the plurality of water tubes 43a alternately in the entire heat exchanger 70.

  The fin 50 is a corrugated fin. The fin 50 has the heat exchange promotion part 50a for promoting heat exchange with the air AR in the center part of the width direction. The heat exchange promoting part 50 a can be provided by a louver 50 a formed on the fin 50. The louver 50 a disturbs the flow of the air AR on the surface of the fin 50. The louver 50 a can have a plurality of slit-shaped openings that penetrate the fins 50. The louver 50a is elongated along the flow direction of the air AR. The louver 50a extends between the refrigerant tube 16a and the water tube 43a so as to partition them.

  The fins 50 are joined to the side surfaces of the refrigerant tube 16a and the water tube 43a by brazing. The fin 50 has the elongate plate-shaped part 50b which does not have the louver 50a along the side surface of the refrigerant | coolant tube 16a and the water tube 43a. The plate-like portion 50b is not cut by the louver 50a. Since the louver 50a is provided by forming a plurality of openings in the fin 50, the louver 50a inhibits heat transfer through the louver 50a. For this reason, the plate-shaped part 50b shows a high heat transfer rate compared with the area | region in which the louver 50a was formed.

  As illustrated, the fin 50 has a frost-resistant end portion 50c. The frost-resistant end portion 50c is an end portion of the fin 50 on the upstream side with respect to the flow direction of the air AR. The frost-resistant end portion 50c is an end portion located on the water tube 43a side with respect to a direction orthogonal to the flow direction of the air AR. The frost resistant end portion 50c is an upstream end portion of the plate-like portion 50b adjacent to the water tube 43a with respect to the flow direction of the air AR.

  The deterioration of the performance of the heat exchanger 70 may occur due to a decrease in the introduction amount of the air AR due to frost adhering to the upstream portion of the heat exchanger 70 in the flow direction of the air AR. The water tube 43a disposed in the upstream portion of the heat exchanger 70 efficiently suppresses the growth of frost or provides heat for removing the frost.

  As shown in the drawing, the high temperature of the water tube 43a is transmitted through the plate-like portion 50b as indicated by the solid arrow. The low temperature of the refrigerant tube 16a is transmitted through the louver 50a as shown by the broken arrow. The thermal conductivity that the fin 50 provides between the water tube 43a and the frost-proof end 50c by the plate-like portion 50b is the heat that the fin 50 provides between the refrigerant tube 16a and the frost-proof end 50c by the louver 50a. Higher than conductivity. For this reason, the heat of the water tube 43a facing the upstream surface of the heat exchanger 70 is efficiently transmitted to the frost-resistant end portion 50c of the fin 50 having the louver 50a. Therefore, the combination of the water tube 43a disposed so as to face the upstream surface of the heat exchanger 70 and the fin 50 having the louver 50a is an end portion of the fin 50 where the heat of the water tube 43a is efficiently transmitted, That is, it contributes to provide the frost-proof end part 50c. The frost-resistant end portion 50c contributes to suppressing a decrease in the amount of air AR introduced due to frost and promoting defrosting.

  FIG. 38 shows a heat exchanger 70 according to this embodiment. In the upstream row, the refrigerant tubes 16a and the water tubes 43a are alternately arranged. Also in this configuration, the heat exchanger 70 has the water tube 43 a facing the upstream surface of the heat exchanger 70. Therefore, the frost-proof end part 50c is provided.

  In the downstream row, only the refrigerant tube 16a is arranged. In other words, in the downstream row, the number of refrigerant tubes 16a is greater than the number of water tubes 43a. The number of refrigerant tubes 16a in the heat exchanger 70 is greater than the number of water tubes 43a. As a result, the flow path cross-sectional area for the outdoor heat exchanger 16 provided by the plurality of refrigerant tubes 16a is larger than the flow path cross-sectional area for the radiator 43 provided by the plurality of water tubes 43a. In the illustrated example, the number of water tubes 43a in the downstream row is zero.

  The refrigerant tube 16a is positioned on the downstream side in the flow direction of the air AR of the water tube 43a belonging to the upstream row. For this reason, the heat transferred from the water tube 43a to the air AR is transferred from the air AR to the refrigerant tube 16a.

  According to this embodiment, the performance of the outdoor heat exchanger 16 in the heat exchanger 70 can be enhanced. Since the number of the refrigerant | coolant tubes 16a can be increased, the pressure loss of the refrigerant path in the outdoor heat exchanger 16 can be suppressed. When the outdoor heat exchanger 16 is used as an evaporator, the low pressure loss greatly contributes to the improvement of the evaporator performance. As a result, it is possible to achieve both an increase in effective heat transfer area and a reduction in pressure loss. Furthermore, since the anti-frosting performance is improved by providing the anti-frost end portion 50c, the high-performance heat exchanger 70 is provided.

(20th embodiment)
Instead of the above embodiment, a plurality of tubes 16a and 43a may be arranged as shown in FIG. In this arrangement, the water tubes 43a are positioned in the downstream row. Therefore, the water tube 43a is not located in the upstream part of the heat exchanger 70 with respect to the flow direction of the air AR. However, no tube is provided on the upstream side of the water tube 43a. Therefore, the water tube 43a faces the upstream side in the flow direction of the air AR in the heat exchanger 70. From another viewpoint, the water tube 43a does not have the refrigerant tube 16a at a position overlapping with the flow direction of the air AR upstream of the water tube 43a itself in the flow direction of the air AR. And the water tube 43a is arrange | positioned so that the refrigerant | coolant tube 16a may be adjoined regarding the direction orthogonal to the flow direction of the air AR. In other words, the water tube 43a is disposed adjacent to the refrigerant tube 16a in the downstream row.

  Even in this configuration, the number of refrigerant tubes 16a in the heat exchanger 70 is larger than the number of water tubes 43a. As a result, the flow path cross-sectional area for the outdoor heat exchanger 16 provided by the plurality of refrigerant tubes 16a is larger than the flow path cross-sectional area for the radiator 43 provided by the plurality of water tubes 43a.

  Even in this configuration, the high temperature of the water tube 43a is transmitted through the plate-like portion 50b as shown by the solid line arrow. The low temperature of the refrigerant tube 16a is transmitted through the louver 50a as shown by the broken arrow. The thermal conductivity that the fin 50 provides between the water tube 43a and the frost-proof end 50c by the plate-like portion 50b is the heat that the fin 50 provides between the refrigerant tube 16a and the frost-proof end 50c by the louver 50a. Higher than conductivity. Therefore, the combination of the water tube 43a disposed so as to face the upstream surface of the heat exchanger 70 and the fin 50 having the louver 50a is an end portion of the fin 50 where the heat of the water tube 43a is efficiently transmitted, That is, the frost-proof end part 50c is provided.

(21st Embodiment)
Instead of the above embodiment, a plurality of tubes 16a and 43a may be arranged as shown in FIG. In this embodiment, instead of the two refrigerant tubes 16a arranged along the flow direction of the air AR, one thick refrigerant tube 16a is employed. Even in this configuration, the flow path cross-sectional area for the outdoor heat exchanger 16 is larger than the flow path cross-sectional area for the radiator 43. The water tube 43a and the fin 50 provide a frost-resistant end portion 50c.

(Twenty-second embodiment)
Instead of the above embodiment, a plurality of tubes 16a, 43a may be arranged as shown in FIG. In this embodiment, the water tube 43a is arranged over both the upstream row and the downstream row. The water tube 43a is disposed between the upstream row and the downstream row. The water tube 43a is adjacent to the refrigerant tube 16a in both the upstream row and the downstream row.

  Even in this configuration, the water tube 43a faces the upstream side in the flow direction of the air AR in the heat exchanger 70. From another viewpoint, the water tube 43a does not have the refrigerant tube 16a at a position overlapping with the flow direction of the air AR upstream of the water tube 43a itself in the flow direction of the air AR. And the water tube 43a is arrange | positioned so that the refrigerant | coolant tube 16a may be adjoined regarding the direction orthogonal to the flow direction of the air AR. In this configuration, the same advantages as those of the above embodiment can be obtained.

(23rd Embodiment)
Instead of the above embodiment, a plurality of tubes 16a, 43a may be arranged as shown in FIG. In this embodiment, instead of the two refrigerant tubes 16a arranged along the flow direction of the air AR, one thick refrigerant tube 16a is employed. In this configuration, the same advantages as those of the above embodiment can be obtained.

(24th Embodiment)
Instead of the above embodiment, a plurality of tubes 16a and 43a may be arranged as shown in FIG. In this embodiment, a water tube 43a having a wider width than the refrigerant tube 16a is employed. The water tube 43a is arranged over both the upstream row and the downstream row. In the upstream row, the water tubes 43a are adjacent so as to overlap only the downstream portion of the refrigerant tube 16a. In the downstream row, the water tubes 43a are adjacent to each other so as to overlap the entire refrigerant tube 16a. In this configuration, the same advantages as those of the above embodiment can be obtained.

(25th Embodiment)
Instead of the above embodiment, a plurality of tubes 16a and 43a may be arranged as shown in FIG. In this embodiment, instead of the two refrigerant tubes 16a arranged along the flow direction of the air AR, one thick refrigerant tube 16a is employed. In this configuration, the same advantages as those of the above embodiment can be obtained.

(Other embodiments)
The preferred embodiments of the disclosed invention have been described above, but the disclosed invention is not limited to the above-described embodiments, and various modifications may be made without departing from the spirit of the disclosed invention. Is possible. The structure of the said embodiment is an illustration to the last, Comprising: The range of the disclosed invention is not limited to the range of these description. The scope of the disclosed invention is indicated by the description of the scope of claims, and further includes all modifications within the meaning and scope equivalent to the description of the scope of claims.

  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 or refrigerant is used as the auxiliary medium. Instead, a fluid that is excellent in heat transportability and can store heat, such as oil or gas, 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 dissipation can be provided so as to be in parallel with the radiator 43 and the external heat source HS.

  In the above embodiment, the air passages 16 b and 43 b are provided in both the outdoor heat exchanger 16 and the radiator 43. However, a configuration in which no air passage is provided in the radiator 43 may be employed. 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.

  In the said embodiment, the apparatus which accumulate | stores the heat from external heat sources, such as an internal combustion engine, and utilizes it for improving the frost-proof performance was comprised. Instead of or in addition to this, the apparatus may be configured to store surplus heat obtained from the refrigerant circuit 10. For example, a heat exchanger that transmits heat of the high-temperature refrigerant before and after the indoor condenser 12 to the cooling water WT can be provided. According to this configuration, it is possible to improve the frost resistance without depending on only the external heat source.

1 air conditioner, 2 heat pump cycle,
10 refrigerant circuit, 40 cooling water circuit,
12 Indoor condenser (use side heat exchanger),
16 outdoor heat exchanger (endothermic heat exchanger),
16a refrigerant tube (cold medium tube),
43 Radiator,
43a water tube (hot medium tube),
50 fins,
70 heat exchanger,
AR air, RF refrigerant, WT cooling water.

Claims (23)

A compressor (11) for supplying high-pressure refrigerant by sucking and compressing low-pressure refrigerant;
A use-side heat exchanger (12) to which the high-pressure refrigerant is supplied and heat is supplied from the high-pressure refrigerant;
A decompressor (13, 213) for depressurizing the high-pressure refrigerant and supplying the low-pressure refrigerant;
An endothermic heat exchanger (16) for exchanging heat between the air (AR) and the low-pressure refrigerant and absorbing the heat to the low-pressure refrigerant;
An auxiliary heat exchanger (43) disposed adjacent to the endothermic heat exchanger and supplying heat to the endothermic heat exchanger;
An auxiliary medium circuit (40) for circulating an auxiliary medium in the auxiliary heat exchanger;
A heat source device (HS, BT) for supplying heat to the auxiliary medium;
A flow rate regulator (41, 42, 44, 45, 442) for regulating the flow rate of the auxiliary medium supplied to the auxiliary heat exchanger;
A controller (100) for controlling the flow rate regulator to change the flow rate according to progress of a heat pump operation that absorbs heat from the endothermic heat exchanger and supplies heat to the use side heat exchanger;
The endothermic heat exchanger (16) and the auxiliary heat exchanger (43) constitute a heat exchanger unit (70) that can be handled as an integral unit,
The endothermic heat exchanger (16) includes a plurality of cold medium tubes (16a),
The auxiliary heat exchanger (43) includes a plurality of hot medium tubes (43a),
The low temperature medium tube and the high temperature medium tube are arranged to be thermally coupled in at least a part of the heat exchanger unit (70),
The low-temperature medium tube and the high-temperature medium tube are arranged to constitute at least an upstream row and a downstream row with respect to the air flow direction,
At least one of the hot medium tubes does not have the cold medium tube at a position overlapping with the air flow direction on the upstream side of the air flow direction from itself, and the air flow direction. With respect to the direction perpendicular to the cryogenic medium tube ,
The heat pump cycle, wherein the low temperature medium tubes and the high temperature medium tubes are alternately arranged in at least a part of the upstream row .   The heat pump cycle according to claim 1, wherein the hot medium tube is not located upstream of the heat exchanger unit (70). The heat pump cycle according to claim 1 or 2, wherein the low-temperature medium tube and the high-temperature medium tube have different widths in the air flow direction . 4. The cold medium tube and the hot medium tube are thermally coupled via fins (50) for exchanging heat with air. Heat pump cycle. A compressor (11) for supplying high-pressure refrigerant by sucking and compressing low-pressure refrigerant;
A use-side heat exchanger (12) to which the high-pressure refrigerant is supplied and heat is supplied from the high-pressure refrigerant;
A decompressor (13, 213) for depressurizing the high-pressure refrigerant and supplying the low-pressure refrigerant;
An endothermic heat exchanger (16) for exchanging heat between the air (AR) and the low-pressure refrigerant and absorbing the heat to the low-pressure refrigerant;
An auxiliary heat exchanger (43) disposed adjacent to the endothermic heat exchanger and supplying heat to the endothermic heat exchanger;
An auxiliary medium circuit (40) for circulating an auxiliary medium in the auxiliary heat exchanger;
A heat source device (HS, BT) for supplying heat to the auxiliary medium;
A flow rate regulator (41, 42, 44, 45, 442) for regulating the flow rate of the auxiliary medium supplied to the auxiliary heat exchanger;
A controller (100) for controlling the flow rate regulator to change the flow rate according to progress of a heat pump operation that absorbs heat from the endothermic heat exchanger and supplies heat to the use side heat exchanger;
The endothermic heat exchanger (16) and the auxiliary heat exchanger (43) constitute a heat exchanger unit (70) that can be handled as an integral unit,
The endothermic heat exchanger (16) includes a plurality of cold medium tubes (16a),
The auxiliary heat exchanger (43) includes a plurality of hot medium tubes (43a),
The low temperature medium tube and the high temperature medium tube are arranged to be thermally coupled in at least a part of the heat exchanger unit (70),
The low-temperature medium tube and the high-temperature medium tube are arranged to constitute at least an upstream row and a downstream row with respect to the air flow direction,
The heat pump cycle, wherein the low temperature medium tubes and the high temperature medium tubes are alternately arranged in at least a part of the upstream row. The heat pump cycle according to claim 5 , wherein the low temperature medium tube and the high temperature medium tube are thermally coupled via fins (50) for exchanging heat with air.   The flow path cross-sectional area for the endothermic heat exchanger provided by the plurality of cold medium tubes is greater than the flow path cross-sectional area for the auxiliary heat exchanger provided by the plurality of hot medium tubes. The heat pump cycle according to any one of claims 1 to 6, wherein the heat pump cycle is characterized. The flow regulator is
A bypass passage (44) for bypassing the auxiliary heat exchanger and flowing the auxiliary medium;
8. A valve device (42, 45, 442) that reduces a flow rate of the auxiliary heat exchanger by flowing the auxiliary medium through the bypass passage. 8. The described heat pump cycle. The controller is
The heat pump cycle according to any one of claims 1 to 8, wherein the flow rate is reduced according to progress of the heat pump operation. The controller is
The heat pump cycle according to claim 9, wherein the flow rate is decreased according to a decrease in a heat load of the heat pump operation. The controller is
Supplying a large flow rate (Gr2) before reaching the boundary between rapid heating and stable heating indicated by the temperature (Rth, Tset) or time (t0-t1) of the air heated by the use side heat exchanger; The heat pump cycle according to claim 9 or 10, wherein a limited flow rate (Grs, Gr1) smaller than the large flow rate is supplied after reaching the boundary. The controller is
The heat pump cycle according to any one of claims 1 to 11, wherein the flow rate is increased in accordance with progress of the heat pump operation. The controller is
The heat pump cycle according to claim 12, wherein the flow rate is increased according to an increase in the amount of frost on the endothermic heat exchanger. The controller is
The flow rate is increased (+ Grfb) in response to temperature (Tp, TAO) or time (t0-t3) indicating an increase in the amount of frost formation on the endothermic heat exchanger. Heat pump cycle. The controller is
The heat pump cycle according to claim 13, wherein the flow rate is increased in accordance with a decrease in refrigerant temperature or refrigerant pressure of the endothermic heat exchanger. The controller is
The heat pump cycle according to any one of claims 1 to 15, wherein the flow rate is increased when the temperature (Tw) of the auxiliary medium rises. The controller is
The flow rate when the temperature (Tw) of the auxiliary medium is higher than a predetermined temperature (Wth1, Wth2) is increased from the flow rate when the temperature (Tw) of the auxiliary medium is lower than a predetermined temperature (Wth1, Wth2) ( The heat pump cycle according to claim 16, wherein + Grfb). The controller is
The flow rate after determining that the endothermic heat exchanger needs to be defrosted is increased (+ Grfb) from the flow rate before determining that the endothermic heat exchanger needs to be defrosted (+ Grfb). The heat pump cycle according to any one of claims 1 to 17. The controller is
After reaching the boundary, the flow rate is increased (+ Grfb) in response to temperature (Tp, TAO) or time (t0-t3) indicating an increase in the amount of frost formation on the endothermic heat exchanger. The heat pump cycle according to claim 11. The controller is
After reaching the boundary, the flow rate when the temperature (Tw) of the auxiliary medium is higher than a predetermined temperature (Wth1, Wth2), and when the temperature (Tw) of the auxiliary medium is lower than the predetermined temperature (Wth1, Wth2). The heat pump cycle according to claim 11 or 19, wherein the heat pump cycle is increased from the flow rate of (+ Grfb). The controller is
After reaching the boundary, the flow rate after determining that the endothermic heat exchanger needs to be defrosted is increased from the flow rate before determining that the endothermic heat exchanger needs to be defrosted. The heat pump cycle according to claim 11, wherein the heat pump cycle is (+ Grfb). The controller is
The flow rate controller is controlled to supply the auxiliary medium to the auxiliary heat exchanger in order to defrost frost adhering to the endothermic heat exchanger after the heat pump operation ends. The heat pump cycle according to any one of claims 1 to 21. Furthermore, a hot gas device (14, 15a, 213) for introducing a high-pressure refrigerant into the endothermic heat exchanger is provided,
23. The heat pump cycle according to claim 22, wherein the control device controls the hot gas equipment to introduce a high-pressure refrigerant into the endothermic heat exchanger when defrosting cannot be performed only with the auxiliary medium.

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