Temperature control device

Abstract

To improve efficiency of temperature regulation in a temperature regulator using a refrigeration cycle and a coolant.SOLUTION: A temperature regulator 1 includes: a refrigeration cycle 10 in which a refrigerant circulates; and a coolant passage 20 in which a coolant circulates. In a water cooling condenser 12, the coolant is heated by the refrigerant. In a chiller 14, the coolant is cooled by the refrigerant. One of the coolant heated by the water cooling condenser 12 and the coolant cooled by the chiller 14 flows through a utilization side heat exchanger to exchange heat with a battery BT and conditioned air CA, and the other exchanges heat with an external heat medium AA in a radiator 31. The coolant passage 20 has a compressor passage 20a for cooling or heating a compressor 11.SELECTED DRAWING: Figure 1

Description

Technical Field

[0001] The present invention relates to a temperature control device including a refrigeration cycle and a cooling water flow path.

Background Art

[0002] Patent Document 1 describes a temperature control device using a refrigeration cycle with a refrigerant and a cooling water flow path. The refrigeration cycle includes a condenser that condenses the refrigerant with the cooling water in the cooling water flow path and a chiller that evaporates the refrigerant with the cooling water in the cooling water flow path. This temperature control device heats the interior of the vehicle and the battery with the cooling water heated by the condenser during heating, and absorbs heat from the cooling water cooled by the chiller in the radiator. Also, during cooling, it cools the interior of the vehicle with the cooling water cooled by the chiller and dissipates heat from the cooling water heated by the condenser in the radiator.

Prior Art Documents

Patent Documents

[0003]

Patent Document 1

Summary of the Invention

Problems to be Solved by the Invention

[0004] According to the inventor's study, in the temperature control device described in Patent Document 1, there is no configuration for cooling the compressor that constitutes the refrigeration cycle, so there is room for improving the efficiency of the temperature control device.

[0005] In view of the above points, an object of the present invention is to improve the efficiency of temperature control in a temperature control device using a refrigeration cycle and cooling water.

Means for Solving the Problems

[0006] The invention according to claim 1 for achieving the above object is a temperature control device for adjusting the temperature of a temperature control target (BT, CA), comprising: a refrigeration cycle (10) in which a refrigerant circulates, A cooling water flow path (20) for supplying cooling water to a utilization-side heat exchanger (32, 33, 34) for heat-exchanging the temperature control target with the cooling water and a radiator (31) for heat-exchanging the heat medium (AA) with the cooling water, The refrigeration cycle includes a compressor (11) that compresses and discharges a refrigerant, a condenser (12) that heats the cooling water by heat-exchanging the refrigerant compressed by the compressor with the cooling water flowing through the cooling water flow path, an expansion valve (13) that decompresses the refrigerant flowing out of the condenser, and a chiller (14) that cools the cooling water by heat-exchanging the refrigerant decompressed by the expansion valve with the cooling water flowing through the cooling water flow path, Of the cooling water heated by the condenser and the cooling water cooled by the chiller, one of the cooling waters flows through the utilization-side heat exchanger and exchanges heat with the temperature control target, and the other cooling water exchanges heat with the heat medium in the radiator, The cooling water flow path has a compressor flow path (20a) for cooling or heating the compressor. and The flow path for the compressor is a temperature control device that is a flow path for heating the compressor with cooling water. The invention according to claim 2 is a temperature control device for adjusting the temperature of a temperature control target (BT, CA), a refrigeration cycle (10) in which a refrigerant circulates, a cooling water flow path (20) for supplying cooling water to a utilization-side heat exchanger (32, 33, 34) for heat-exchanging the temperature control target and cooling water, a radiator (31) for heat-exchanging the heat medium (AA) and the cooling water, and the cooling water, The refrigeration cycle includes a compressor (11) that compresses and discharges a refrigerant, a condenser (12) that heats the cooling water by heat-exchanging the refrigerant compressed by the compressor and the cooling water flowing through the cooling water flow path, an expansion valve (13) that decompresses the refrigerant flowing out from the condenser, and a chiller (14) that cools the cooling water by heat-exchanging the refrigerant decompressed by the expansion valve and the cooling water flowing through the cooling water flow path. Of the cooling water heated by the condenser and the cooling water cooled by the chiller, one cooling water flows through the utilization-side heat exchanger and exchanges heat with the temperature control target, and the other cooling water exchanges heat with the heat medium in the radiator. The cooling water flow path has a compressor flow path (20a) for cooling or heating the compressor. In the hot water utilization mode, the cooling water heated by the condenser warms the temperature control target in the utilization-side heat exchanger, and the cooling water cooled by the chiller absorbs heat in the radiator. In the hot water utilization mode, when there is no frosting on the radiator, it is a temperature control device in which the cooling water circulates through the compressor flow path after being cooled by the chiller and before being heated by the radiator. The invention according to claim 3 is a temperature control device for adjusting the temperature of a temperature control target (BT, CA), a refrigeration cycle (10) in which a refrigerant circulates, a cooling water flow path (20) for supplying cooling water to a utilization-side heat exchanger (32, 33, 34) for heat-exchanging the temperature control target and cooling water, a radiator (31) for heat-exchanging the heat medium (AA) and the cooling water, and the cooling water, The refrigeration cycle includes a compressor (11) that compresses and discharges a refrigerant, a condenser (12) that heats cooling water by exchanging heat between the refrigerant compressed by the compressor and the cooling water flowing through the cooling water flow path, an expansion valve (13) that decompresses the refrigerant flowing out from the condenser, and a chiller (14) that cools the cooling water by exchanging heat between the refrigerant decompressed by the expansion valve and the cooling water flowing through the cooling water flow path. Of the cooling water heated by the condenser and the cooling water cooled by the chiller, one of the cooling waters flows through the utilization-side heat exchanger and exchanges heat with the temperature control target, and the other cooling water exchanges heat with the heat medium in the radiator. The cooling water flow path has a compressor flow path (20a) for cooling or heating the compressor. The temperature control device is a temperature control device having a multi-switching mechanism (23, 28, 30, 36, 41, 61, 62) that switches a path for guiding cooling water to the compressor flow path in the cooling water flow path. Further, the invention according to claim 4 is a temperature control device that adjusts the temperature of a temperature control target (BT, CA), a refrigeration cycle (10) in which a refrigerant circulates, a utilization-side heat exchanger (32, 33, 34) for exchanging heat between the temperature control target and cooling water, and a cooling water flow path (20) for supplying cooling water to a radiator (31) for exchanging heat between the heat medium (AA) and the cooling water. The refrigeration cycle includes a compressor (11) that compresses and discharges a refrigerant, a condenser (12) that heats cooling water by exchanging heat between the refrigerant compressed by the compressor and the cooling water flowing through the cooling water flow path, an expansion valve (13) that decompresses the refrigerant flowing out from the condenser, and a chiller (14) that cools the cooling water by exchanging heat between the refrigerant decompressed by the expansion valve and the cooling water flowing through the cooling water flow path. Of the cooling water heated by the condenser and the cooling water cooled by the chiller, one of the cooling waters flows through the utilization-side heat exchanger and exchanges heat with the temperature control target, and the other cooling water exchanges heat with the heat medium in the radiator. The cooling water flow path has a compressor flow path (20a) for cooling or heating the compressor. The compressor has a housing (125) and a movable member (141) surrounded by the housing. A compression chamber (423) is formed between the housing and the movable member. When the movable member moves, the refrigerant is introduced from the suction port (422) into the compression chamber, compressed in the compression chamber, and then discharged from the discharge port (421). The flow path for the compressor has a heat exchange passage (853) formed inside the housing. The flow path for the compressor is a flow path for cooling the compressor. In a portion of the housing closer to the discharge port than the suction port, the surface area of the heat exchange passage per unit volume is larger than the surface area of the heat exchange passage per unit volume in a portion of the housing closer to the suction port than the discharge port. This is a temperature control device.

[0007] By being configured in this way, the compressor can be cooled or heated using cooling water. As a result, the efficiency of temperature control can be improved.

[0008] Note that the reference signs with parentheses attached to each component etc. indicate an example of the correspondence relationship between the component etc. and the specific components etc. described in the embodiments described later.

Brief Description of the Drawings

[0009]

Figure 1

Figure 2

Figure 3

Figure 4

Figure 5

Figure 6

Figure 7

Figure 8

Figure 9

Figure 10

Figure 11

Figure 12

Figure 13

Figure 14

Figure 15

Figure 16

Figure 17

Figure 18

Figure 19

Figure 20

Figure 21

Figure 22

Figure 23

Figure 24

Figure 25

Figure 26

Figure 27

Figure 28

Figure 29

Mode for Carrying Out the Invention

[0010] Hereinafter, embodiments of the present disclosure will be described. In the following embodiments, parts that are the same as or equivalent to those described in the preceding embodiments may be given the same reference numerals, and the description thereof may be omitted. Further, in the embodiments, when only a part of the components is described, the components described in the preceding embodiments can be applied to the other parts of the components. The following embodiments can be partially combined with each other as long as there is no problem in the combination, even if not particularly specified.

[0011] (First Embodiment) Hereinafter, the first embodiment will be described. The temperature control device 1 shown in FIG. 1 is mounted on a vehicle and adjusts the temperature of the battery BT which is the object of temperature control in the vehicle and the air-conditioning air CA sent to the vehicle interior space. The battery BT is, for example, a power source for an electric motor that generates power for the running of the vehicle.

[0012] The temperature control device 1 includes a refrigeration cycle 10 through which a refrigerant flows and a cooling water flow path 20 through which cooling water flows. As the refrigerant, for example, a fluorocarbon refrigerant such as HFO134a is used. As the cooling water, for example, a liquid such as an antifreeze containing water and ethylene glycol is used, but other liquids may also be used.

[0013] The refrigeration cycle 10 includes a compressor 11, a water-cooled condenser 12, an expansion valve 13, a chiller 14, and a refrigerant flow path connecting them. The compressor 11 has a compression mechanism 11a, a motor 11b, and an inverter circuit 11c.

[0014] The compression mechanism 11a is a mechanism having a mechanism that introduces and compresses a refrigerant and discharges the compressed refrigerant at a high temperature and high pressure. The motor 11b is an electric motor that generates power for driving the compression mechanism. The inverter circuit 11c is a circuit that supplies power for power generation to the motor 11b.

[0015] The water-cooled condenser 12 is a heat exchanger having a flow path through which the refrigerant flows and a flow path through which the cooling water flows. The water-cooled condenser 12 has the high-temperature and high-pressure refrigerant discharged from the compressor 11 flowing therein, and also has the cooling water flowing in from the cooling water flow path 20. Then, in the water-cooled condenser 12, heat exchange occurs between these refrigerant and the cooling water. As a result, the refrigerant dissipates heat and condenses, and the cooling water is heated.

[0016] The expansion valve 13 is a throttle valve that decompresses and expands the refrigerant flowing out from the water-cooled condenser 12 and passes it to the chiller 14. The chiller 14 is a heat exchanger having a flow path through which the refrigerant flows and a flow path through which the cooling water flows. The chiller 14 has the refrigerant that has passed through the expansion valve 13 flowing therein, and also has the cooling water flowing in from the cooling water flow path 20. Then, in the chiller 14, heat exchange occurs between these refrigerant and the cooling water. As a result, the refrigerant absorbs heat and evaporates, and the cooling water is cooled. The refrigerant flowing out from the chiller 14 is sucked into the compressor 11.

[0017] In this way, in the refrigeration cycle 10, the refrigerant circulates in the order of the compressor 11, the water-cooled condenser 12, the expansion valve 13, and the chiller 14, thereby heating the cooling water in the water-cooled condenser 12 and cooling the cooling water in the chiller 14.

[0018] The cooling water flow path 20 has a first pump 21, a second pump 22, a first three-way valve 23, a second three-way valve 24, a third three-way valve 25, a fourth three-way valve 26, a fifth three-way valve 27, and a sixth three-way valve 28. Further, the cooling water flow path 20 has a first shut-off valve 29, a second shut-off valve 30, a radiator 31, a cooler core 32, a heater core 33, and a battery heat exchanger 34.

[0019] The cooling water flow path 20 has a flow path for circulating the cooling water between these devices. The cooling water flow path 20 has a compressor flow path 20a that flows inside the compressor 11 and a flow path that flows outside the compressor 11 and communicates with both ends of the compressor flow path 20a.

[0020] The compressor flow path 20a is disposed in the compressor 11 in the vicinity of the compression mechanism 11a. Thereby, in the compressor flow path 20a, heat exchange is possible between the compression mechanism 11a and the cooling water.

[0021] The first pump 21 is an electric pump that sucks and pumps the cooling water. The cooling water pumped by the first pump 21 passes through the water-cooled condenser 12, and during this passage, it absorbs heat from the refrigerant in the water-cooled condenser 12 as described above. The second pump 22 is an electric pump that sucks and pumps the cooling water. The cooling water pumped by the second pump 22 heads toward the sixth three-way valve 28 and the chiller 14 side.

[0022] The first three-way valve 23 is a control valve that switches the presence or absence of the flow of the cooling water that has flowed out after being cooled by the chiller 14 to the utilization side and the presence or absence of the flow to the radiator 31 side. Here, the utilization side refers to the side of the heat exchanger for heat exchange with the battery BT and the air-conditioning air CA sent into the vehicle interior. The utilization side is generally the side of the cooler core 32, the heater core 33, and the battery heat exchanger 34, but for the first three-way valve 23, it is the side of the cooler core 32 and the battery heat exchanger 34. The cooler core 32, the heater core 33, and the battery heat exchanger 34 respectively correspond to the utilization-side heat exchangers.

[0023] The second three-way valve 24 is a control valve that switches the presence or absence of the flow of the cooling water flowing out from the first three-way valve 23 to the utilization side to the battery heat exchanger 34 and the presence or absence of the flow to the cooler core 32. The third three-way valve 25 is a control valve that switches the presence or absence of the flow of the cooling water heated by the water-cooled condenser 12 to the heater core 33 and the presence or absence of the flow to the radiator 31 side.

[0024] The third-party valve 26 is a control valve that switches the presence or absence of the flow of the cooling water heat-exchanged with the external heat medium AA in the radiator 31 to the first pump 21 and the water-cooled condenser 12 side, and the presence or absence of the flow to the second pump 22 and the chiller 14 side. The external heat medium AA is a heat medium in the external environment such as the air outside the vehicle cabin.

[0025] The fifth third-party valve 27 is a control valve that switches the presence or absence of the flow of the cooling water heat-exchanged with the battery in the battery heat exchanger 34 to the first pump 21 and the water-cooled condenser 12 side, and the presence or absence of the flow to the second pump 22 and the chiller 14 side. The sixth third-party valve 28 is a control valve that switches the presence or absence of the flow of the cooling water pumped from the second pump 22 to the chiller 14 side, and the presence or absence of the flow to the inflow side end of the compressor flow path 20a.

[0026] The first shut-off valve 29 is a control valve that switches the flow and cutoff of the cooling water between the water-cooled condenser 12 and the battery heat exchanger 34. The second shut-off valve 30 is a control valve that switches the flow and cutoff of the cooling water between the inflow side end of the compressor flow path 20a and the chiller 14. Note that the outflow side end of the compressor flow path 20a communicates in parallel with the inflow side end of the second shut-off valve 30 and the radiator 31.

[0027] The radiator 31 is a heat exchanger that has a flow path through which the cooling water flows and exchanges heat between the external heat medium AA and the cooling water. The radiator 31 absorbs heat from the external heat medium AA to the cooling water in the warm water utilization mode described later, and dissipates heat from the cooling water to the external medium in the cold water utilization mode described later.

[0028] Both the cooler core 32 and the heater core 33 are heat exchangers that have a flow path through which the cooling water flows and are arranged in the air-conditioning casing 35. The inflow side end of the cooler core 32 communicates with the second third-party valve 24, and the outflow side end communicates with the suction side of the second pump 22. The inflow side end of the heater core 33 communicates with the third third-party valve 25, and the outflow side end communicates with the suction side of the first pump 21.

[0029] In the cold water utilization mode, inside the air conditioning casing 35, the conditioned air CA blown into the vehicle interior by a blower (not shown) is cooled by exchanging heat with the cooling water flowing through the cooler core 32. In the hot water utilization mode, inside the air conditioning casing 35, the conditioned air CA blown into the vehicle interior by a blower (not shown) is heated by exchanging heat with the cooling water flowing through the heater core 33. The conditioned air CA corresponds to the object to be temperature-controlled.

[0030] The heat exchanger 34 for the battery is provided with a flow path through which the cooling water flows and is arranged near the battery BT. In the cold water utilization mode, the battery BT is cooled by exchanging heat with the cooling water flowing through the heat exchanger 34 for the battery. In the hot water utilization mode, the battery BT is heated by exchanging heat with the cooling water flowing through the heat exchanger 34 for the battery. The battery BT corresponds to the object to be temperature-controlled.

[0031] Hereinafter, the operation of the temperature control device 1 configured as described above will be described. First, the operation of the controlled devices such as the compressor 11, the pumps 21 and 22, the three-way valves 23 to 28, and the shut-off valves 29 and 30 is controlled by a control circuit (not shown). Specifically, the control circuit determines whether to execute the hot water utilization mode or the cold water utilization mode based on the amounts acquired from various sensors (not shown), and controls the above-described controlled devices according to the determination result.

[0032] Examples of the various sensors include, but are not limited to, an outside air temperature sensor that detects the temperature outside the vehicle, an inside air temperature sensor that detects the temperature inside the vehicle, a battery temperature sensor that detects the temperature of the battery BT, and an operation unit that receives user operations such as temperature setting.

[0033] For example, the control circuit may determine whether to execute the hot water utilization mode or the cold water utilization mode based on a well-known target blow-out temperature TAO calculated based on the temperature outside the vehicle, the temperature inside the vehicle, the set temperature by the user, and the like. Basically, when it is necessary to warm the utilization side, the control circuit executes the hot water utilization mode, and when it is necessary to cool the utilization side, the control circuit executes the cold water utilization mode.

[0034] [Hot water utilization mode] Here, the hot water utilization mode will be described. When the hot water utilization mode is executed, the control circuit operates the compressor 11, pumps 21 and 22. Further, as shown in FIG. 2, the control circuit controls the first three-way valve 23 such that the cooling water flows from the chiller 14 to the compressor 11 and the passage between the first three-way valve 23 and the second three-way valve 24 is blocked. Further, the control circuit controls the second three-way valve 24 such that the passage between the battery heat exchanger 34 and the cooler core 32 is blocked. Further, the control circuit controls the third three-way valve 25 such that the cooling water flows from the water-cooled condenser 12 to the heater core 33 and the passage between the third three-way valve 25 and the radiator 31 is blocked.

[0035] Further, the control circuit controls the fourth three-way valve 26 such that the cooling water flows from the radiator 31 to the second pump 22 and the passage between the fourth three-way valve 26 and the first pump 21 is blocked. Further, the control circuit controls the fifth three-way valve 27 such that the cooling water flows from the battery heat exchanger 34 to the first pump 21 and the passage between the fifth three-way valve 27 and the second pump 22 is blocked. Further, the control circuit controls the sixth three-way valve 28 such that the cooling water flows from the second pump 22 to the chiller 14 and the passage between the sixth three-way valve 28 and the compressor flow path 20a is blocked. Further, the control circuit opens the shut-off valve 29 and closes the second shut-off valve 30.

[0036] As a result, as shown in FIG. 2, the cooling water, i.e., the hot water, heated by the water-cooled condenser 12 flows into the heater core 33 via the third three-way valve 25 and also flows into the battery heat exchanger 34 via the first shut-off valve 29. Thereby, the hot water warms the air-conditioning air CA in the heater core 33, and heating in the vehicle interior is realized. Also, the hot water heats the battery BT in the battery heat exchanger 34.

[0037] The cooling water flowing out from the heater core 33 flows into the suction side of the first pump 21, and is further urged by the first pump 21 to return to the water-cooled condenser 12. Also, the cooling water flowing out from the battery heat exchanger 34 merges with the cooling water flowing out from the heater core 33 after passing through the fifth three-way valve 27, and is further urged by the first pump 21 as described above to return to the water-cooled condenser 12.

[0038] In this way, the circuits that circulate like the water-cooled condenser 12, the third three-way valve 25, the heater core 33, the first pump 21, and the water-cooled condenser 12 function as a hot water circuit. Also, the circuits that circulate like the water-cooled condenser 12, the first shut-off valve 29, the battery heat exchanger 34, the fifth three-way valve 27, the first pump 21, and the water-cooled condenser 12 function as a hot water circuit.

[0039] Also, as shown in FIG. 2, the cooling water, i.e., cold water, cooled by the chiller 14 flows into the compressor flow path 20a via the first three-way valve 23, cools the compressor 11 there, and then flows out of the compressor flow path 20a and into the radiator 31. In the compressor 11, the cooling water flows through the position closest to the compression mechanism 11a among the compression mechanism 11a, the motor 11b, and the inverter circuit 11c to cool the compression mechanism 11a.

[0040] The cold water that has flowed into the radiator 31 absorbs heat by exchanging heat with the external heat medium AA in the radiator 31. That is, the cold heat is discharged to the external heat medium AA. The cooling water that has flowed out of the radiator 31 flows into the suction side of the second pump 22 via the fourth three-way valve 26, and is further urged by the second pump 22 to return to the chiller 14 via the sixth three-way valve 28.

[0041] In this way, the circuits that circulate like the chiller 14, the first three-way valve 23, the compressor flow path 20a, the radiator 31, the fourth three-way valve 26, the second pump 22, the sixth three-way valve 28, and the chiller 14 function as a cold water circuit.

[0042] In this way, in the hot water utilization mode, the cold heat of the cooling water is discarded to the external heat medium AA by the radiator 31, and the heat of the cooling water warms the temperature control target by the battery heat exchanger 34 and the heater core 33. And in the cold water circuit, the cooling water passes through the compressor flow path 20a to cool the compressor 11.

[0043] That is, in the cold water circuit, the path from the first three-way valve 23 to the inflow side end of the compressor flow path 20a and the path from the outflow side end of the compressor flow path 20a to the radiator 31 form the first cooling path for guiding cooling water to the compressor flow path 20a.

[0044] And in the compressor flow path 20a, the cooling water after being cooled by the chiller 14 and before radiating heat to the radiator 31 cools the compressor 11. Thereby, the cold heat immediately before being discarded by the radiator 31 can be effectively utilized. Also, the compressor 11 can be cooled by the cooling water in a lower temperature state before absorbing heat by the radiator 31.

[0045] In addition, as another example, in the hot water utilization mode, when the control circuit determines that it is not necessary to warm the battery BT according to the temperature of the battery BT, the shut-off valve 29 may be closed. In that case, only the circuit that circulates the above-mentioned water-cooled condenser 12 and the heater core 33 functions as the hot water circuit.

[0046] Also, as another example, in the hot water utilization mode, when the control circuit determines that it is not necessary to warm the air-conditioning air CA, the port on the radiator 31 side and the port on the heater core 33 side of the third three-way valve 25 may be blocked. In that case, only the circuit that circulates the above-mentioned water-cooled condenser 12 and the battery heat exchanger 34 functions as the hot water circuit.

[0047] Also, as another example, in the hot water utilization mode, when the control circuit determines that it is necessary to cool the battery BT instead of heating it according to the temperature of the battery BT, the control circuit may control to flow the cold water cooled by the chiller 14 to the battery heat exchanger 34. In this control, the first shutoff valve 29 is closed, the ports on the second three-way valve 24 side and the radiator 31 side of the first three-way valve 23 are opened, the port on the first pump 21 side of the fifth three-way valve 27 is closed, and the port on the second pump 22 side is opened. As a result, the circuit that circulates in the order of the chiller 14, the first three-way valve 23, the second three-way valve 24, the battery heat exchanger 34, the fifth three-way valve 27, the second pump 22, the sixth three-way valve 28, and the chiller 14 also functions as a cold water circuit. And at this time, only the circuit that circulates the above-described water-cooled condenser 12 and the heater core 33 functions as a hot water circuit.

[0048] [Cold water utilization mode] Next, the cold water utilization mode will be described. When executing the cold water utilization mode, the control circuit operates the compressor 11, the pumps 21, and 22. Further, as shown in FIG. 3, the control circuit controls the first three-way valve 23 such that cooling water flows from the chiller 14 to the second three-way valve 24 and the space between the first three-way valve 23 and the compressor 11 is blocked. Further, the control circuit controls the second three-way valve 24 such that cooling water flows from the first three-way valve 23 to the cooler core 32 and the battery heat exchanger 34. Further, the control circuit controls the third three-way valve 25 such that cooling water flows from the water-cooled condenser 12 to the radiator 31 and the space between the third three-way valve 25 and the heater core 33 is blocked.

[0049] Furthermore, the control circuit controls the fourth three-way valve 26 such that cooling water flows from the radiator 31 to the first pump 21 and the space between the fourth three-way valve 26 and the second pump 22 is blocked. Further, the control circuit controls the fifth three-way valve 27 such that cooling water flows from the battery heat exchanger 34 to the second pump 22 and the space between the fifth three-way valve 27 and the first pump 21 is blocked. Further, the control circuit controls the sixth three-way valve 28 such that cooling water flows from the second pump 22 to the compressor flow path 20a and the space between the sixth three-way valve 28 and the chiller 14 is blocked. Further, the control circuit closes the shutoff valve 29 and opens the second shutoff valve 30.

[0050] As a result, as shown in FIG. 3, the cooling water, i.e., the warm water, heated by the water-cooled condenser 12 flows into the radiator 31 via the third three-way valve 25. Thereby, waste heat is transferred from the warm water to the external heat medium AA in the radiator 31. The cooling water whose temperature has decreased after heat exchange with the external heat medium AA in the radiator 31 flows into the suction side of the first pump 21 via the fourth three-way valve 26, and is further urged by the first pump 21 to return to the water-cooled condenser 12.

[0051] In this way, the circuit that circulates like the water-cooled condenser 12, the third three-way valve 25, the radiator 31, the fourth three-way valve 26, the first pump 21, and the water-cooled condenser 12 functions as a warm water circuit.

[0052] Also, as shown in FIG. 3, the cooling water, i.e., the cold water, cooled by the chiller 14 flows into the second three-way valve 24 via the first three-way valve 23, and branches at the second three-way valve 24 and flows out to the cooler core 32 side and the battery heat exchanger 34 side. The cold water flowing into the cooler core 32 cools the air-conditioning air CA, thereby realizing cooling in the vehicle interior. The cold water flowing into the battery heat exchanger 34 cools the battery BT.

[0053] The cooling water flowing out of the cooler core 32 flows into the suction side of the second pump 22. Also, the cooling water flowing out of the battery heat exchanger 34 merges with the cooling water flowing out of the cooler core 32 via the fifth three-way valve 27, and further flows into the suction side of the second pump 22.

[0054] The cooling water flowing into the second pump 22 is urged by the second pump 22 and flows into the compressor flow path 20a via the sixth three-way valve 28, where it cools the compression mechanism 11a of the compressor 11. Further, the cooling water returns from the compressor flow path 20a to the chiller 14 through the second shut-off valve 30.

[0055] In this way, the circuit that circulates like the chiller 14, the first three-way valve 23, the second three-way valve 24, the cooler core 32, the second pump 22, the sixth three-way valve 28, the compressor flow path 20a, and the chiller 14 functions as a chilled water circuit. Also, the circuit that circulates like the chiller 14, the first three-way valve 23, the second three-way valve 24, the battery heat exchanger 34, the fifth three-way valve 27, the second pump 22, the sixth three-way valve 28, the compressor flow path 20a, and the chiller 14 functions as a chilled water circuit.

[0056] In this way, in the chilled water utilization mode, the waste heat of the warm water is discarded to the external heat medium AA by the radiator 31, and the chilled water cools the object to be temperature-controlled by the battery heat exchanger 34 and the cooler core 32. Then, in the chilled water circuit, the cooling water passes through the compressor flow path 20a to cool the compressor 11.

[0057] That is, among the chilled water circuit, the path from the sixth three-way valve 28 to the inflow side end of the compressor flow path 20a and the path from the outflow side end of the compressor flow path 20a to the chiller 14 form the second cooling path for guiding the cooling water to the compressor flow path 20a.

[0058] And in the compressor flow path 20a, since the cooling water that has cooled the battery BT and the air-conditioning air CA that should originally be cooled in the chilled water utilization mode cools the compressor 11, it is possible to cool the compressor 11 while suppressing the influence of the cooling of the compressor 11 on the cooling performance of the battery BT and the air-conditioning air CA.

[0059] Note that as another example, in the chilled water utilization mode, the control circuit may determine that it is not necessary to cool the battery BT according to the temperature of the battery BT. In that case, the control circuit may close the port on the battery heat exchanger 34 side of the second three-way valve 24 so that the cooling water does not flow from the second three-way valve 24 to the battery heat exchanger 34. Thereby, only the circuit that circulates the above-mentioned water-cooled condenser 12 and the cooler core 32 functions as a chilled water circuit.

[0060] Also, as another example, in the cold water utilization mode, when the control circuit determines that it is not necessary to cool the air-conditioning air CA, the port on the cooler core 32 side of the second three-way valve 24 may be closed so that cooling water does not flow from the second three-way valve 24 to the cooler core 32. In that case, only the circuit that circulates the above-described water-cooled condenser 12 and the battery heat exchanger 34 functions as the cold water circuit.

[0061] Also, as another example, in the cold water utilization mode, when the control circuit determines that it is necessary to warm the battery BT according to the temperature of the battery BT, the control circuit may perform control to cause the warm water heated by the water-cooled condenser 12 to flow to the battery heat exchanger 34. In this control, the first shut-off valve 29 is opened, and at the fifth three-way valve 27, the port on the second pump 22 side is closed and the port on the first pump 21 side is opened. Also, in this control, the port on the battery heat exchanger 34 side of the second three-way valve 24 is closed so that cooling water does not flow from the second three-way valve 24 to the battery heat exchanger 34. As a result, the circuit that circulates in the order of the water-cooled condenser 12, the first shut-off valve 29, the battery heat exchanger 34, the fifth three-way valve 27, the first pump 21, and the water-cooled condenser 12 also functions as a warm water circuit. Also, only the circuit that circulates the above-described chiller 14 and the cooler core 32 functions as the cold water circuit.

[0062] As described above, the cooling water flow path 20 has a compressor flow path 20a for cooling the compressor 11. By being configured in this way, the compressor 11 can be cooled using cooling water. As a result, the efficiency of temperature control can be improved.

[0063] (1) Also, both the first cooling path in the warm water utilization mode and the second cooling path in the cold water utilization mode are configured such that the cooling water cooled by the chiller 14 flows through the compressor flow path 20a. By being configured in this way, the compressor can be cooled with cooler cooling water.

[0064] (2) Further, the first three-way valve 23, the sixth three-way valve 28, and the second shut-off valve 30 constitute a multi-switching mechanism that switches the path for guiding cooling water to the compressor flow path 20a in the cooling water flow path 20. By introducing cooling water into the compressor flow path 20a using different paths of the cooling water flow path 20 in this way, it is possible to supply cooling water suitable for the usage scene.

[0065] (3) More specifically, the multi-switching mechanism switches between the first cooling path and the second cooling path. As described above, the first cooling path is a path that guides the cooling water cooled by the chiller 14 to the compressor flow path 20a before flowing into the radiator 31. The second cooling path is a path that guides the cooling water cooled by the chiller 14 to the compressor flow path 20a after flowing into the utilization-side heat exchanger and before returning to the chiller 14.

[0066] By doing so, in the first cooling circuit, the cold heat before being discarded to the external heat medium AA by the radiator 31 can be effectively utilized to cool the compressor 11. Also, in the second cooling circuit, the compressor 11 is cooled by the cooling water after being used in the utilization-side heat exchanger. Therefore, the influence on the temperature control target by cooling the compressor with cooling water can be suppressed.

[0067] (Second Embodiment) Next, the second embodiment will be described with reference to FIGS. 4, 5, and 6. In the temperature control device 1 of this embodiment, the configuration of the cooling water flow path 20 is partially changed compared to the first embodiment. Specifically, as shown in FIG. 4, a seventh three-way valve 36 and a bypass flow path 37 that bypasses the compressor flow path 20a from the seventh three-way valve 36 and allows cooling water to flow to the radiator 31 are provided in the flow path on the radiator 31 side of the first three-way valve 23. The other configurations are the same as those in the first embodiment.

[0068] The seventh three-way valve 36 is a control valve that switches the presence or absence of the cooling water flowing out from the port on the compressor flow path 20a side of the first three-way valve 23 to the compressor flow path 20a and the presence or absence of the flow to the radiator 31 via the bypass flow path 37. This seventh three-way valve 36 is controlled by the control circuit described in the first embodiment. The bypass flow path 37 is a flow path for bypassing the compressor flow path 20a with the cooling water flowing out from the chiller 14 and allowing it to flow into the radiator 31. The seventh three-way valve 36 corresponds to the cold non-switching mechanism.

[0069] Hereinafter, the operation of the temperature control device 1 in this embodiment will be described. The operation of the temperature control device 1 in the cold water utilization mode is the same as that in the first embodiment. However, at this time, the control circuit closes the port on the compressor flow path 20a side and the port on the bypass flow path 37 side for the seventh three-way valve 36.

[0070] In the hot water utilization mode, the control circuit switches the flow path configuration of the cold water circuit according to the temperature of the compressor 11, the temperature outside the vehicle compartment, etc. For example, the control circuit may specify the temperature of the compressor 11 based on detection signals from, for example, a cooling water temperature sensor, a compressor temperature sensor, an outside air temperature sensor, etc. The cooling water temperature sensor detects the temperature of the cooling water after passing through the compressor flow path 20a and before entering the radiator 31. The compressor temperature sensor is arranged, for example, near the compression mechanism 11a to detect the temperature of the compression mechanism 11a.

[0071] For example, when the temperature of the compressor 11 is higher than a predetermined temperature and cooling is required, the control circuit realizes a flow path configuration as shown in FIG. 5. Alternatively, when the temperature outside the vehicle compartment is higher than the reference temperature and the compressor 11 needs to be cooled, the control circuit realizes a flow path configuration as shown in FIG. 5. Specifically, for the compressor 11, the pumps 21, 22, the three-way valves 23 to 28, and the shut-off valves 29, 30, they are controlled in the same manner as in the hot water utilization mode of the first embodiment. Further, for the seventh three-way valve 36, it is controlled as follows.

[0072] That is, control is performed so that the cooling water flowing from the first three-way valve 23 to the seventh three-way valve 36 does not flow out to the bypass flow path 37 but flows out to the compressor 11 side. This is achieved by opening the port on the compressor 11 side of the seventh three-way valve 36 and closing the port on the bypass flow path 37 side. In this case, a hot water circuit and a cold water circuit having the same configuration as in the hot water utilization mode of the first embodiment are realized. However, with respect to the cold water circuit, the cooling water passes through the seventh three-way valve 36 after passing through the first three-way valve 23 and flows into the compressor 11. Due to such a flow of the cold water circuit, the compressor 11 is cooled by the cooling water.

[0073] Also, for example, when the temperature of the compressor 11 is lower than the predetermined temperature and there is no need to cool it, the control circuit realizes a flow path configuration as shown in FIG. 6. Alternatively, when the temperature outside the vehicle is lower than the reference temperature and there is no need to cool the compressor 11, the control circuit realizes a flow path configuration as shown in FIG. 6. Specifically, with respect to the pumps 21 and 22, the three-way valves 23 to 28, and the shut-off valves 29 and 30, control is performed in the same manner as in the hot water utilization mode of the first embodiment. Further, with respect to the seventh three-way valve 36, control is performed as follows.

[0074] That is, control is performed so that the cooling water flowing from the first three-way valve 23 to the seventh three-way valve 36 does not flow out to the compressor flow path 20a side but flows out to the bypass flow path 37. This is achieved by closing the port on the compressor flow path 20a side of the seventh three-way valve 36 and opening the port on the bypass flow path 37 side. In this case, with respect to the hot water circuit, the same configuration as in the hot water utilization mode of the first embodiment is realized.

[0075] Also, with respect to the cold water circuit, a cold water circuit is realized in which the chiller 14, the first three-way valve 23, the seventh three-way valve 36, the bypass flow path 37, the radiator 31, the fourth three-way valve 26, the pump 22, the sixth three-way valve 28, and the chiller 14 circulate in this order to bypass the compressor flow path 20a. Thereby, the possibility of unnecessarily cooling the compressor 11 is reduced.

[0076] (1) As described above, the seventh three-way valve 36 switches between a path through which the cooling water cooled by the chiller 14 cools the compressor 11 and flows into the radiator 31, and a path through which the cooling water cooled by the chiller 14 bypasses the compressor 11 and flows into the radiator 31.

[0077] The compressor 11 does not necessarily need to be constantly cooled during operation. For example, in an extremely low-temperature environment, excessive cooling of the compressor 11 may increase the frictional loss of the compression mechanism 11a. Therefore, having a mechanism to switch whether to cool the compressor 11 with cooling water enables the proper operation of the temperature control device 1. Note that, in this embodiment, the same configuration as in the first embodiment provides the same effects.

[0078] In this embodiment, the first three-way valve 23, the sixth three-way valve 28, the seventh three-way valve 36, and the second shut-off valve 30 constitute a multi-switching mechanism that switches the path for guiding cooling water to the compressor flow path 20a in the cooling water flow path 20. And, in the cold water circuit in the hot water utilization mode, the path from the seventh three-way valve 36 to the inflow side end of the compressor flow path 20a and the path from the outflow side end of the compressor flow path 20a to the radiator 31 form the first cooling path. And, in the cold water circuit in the cold water utilization mode, the path from the sixth three-way valve 28 to the inflow side end of the compressor flow path 20a and the path from the outflow side end of the compressor flow path 20a to the chiller 14 form the second cooling path.

[0079] (Third Embodiment) Next, the third embodiment will be described with reference to FIG. 7. In this embodiment, the configuration of the compressor flow path 20a is different from that of the temperature control device 1 of the first embodiment. Specifically, as shown in FIG. 7, the compressor flow path 20a includes a flow path that passes near the compression mechanism 11a and exchanges heat between the compression mechanism 11a and the cooling water, and a flow path that passes near the inverter circuit 11c and exchanges heat between the inverter circuit 11c and the cooling water. These flow paths may be configured in series as shown in FIG. 7, or may be configured in parallel.

[0080] Other configurations are the same as those in the first embodiment. Also, in the flow path outside the compressor flow path 20a in the cooling water flow path 20, the path through which the cooling water flows in the cold water utilization mode and the hot water utilization mode is the same as that in the first embodiment.

[0081] Thus, in both the cold water utilization mode and the hot water utilization mode, the cooling water flowing into the compressor flow path 20a cools the compression mechanism 11a and the inverter circuit 11c in the compressor flow path 20a.

[0082] (1) As described above, the compressor flow path 20a includes a flow path for cooling the inverter circuit 11c. By doing so, the inverter circuit 11c, which has a large heat generation amount and is easily affected by heat, can be effectively cooled.

[0083] Note that changes such as those in this embodiment with respect to the first embodiment are also applicable to the second embodiment. Also, in this embodiment, the same effects can be obtained from the same configurations as those in the first and second embodiments.

[0084] (Fourth Embodiment) Next, the fourth embodiment will be described with reference to FIG. 8. In this embodiment, for the temperature control device 1 of the first embodiment, the pair of the first three-way valve 23 and the second three-way valve 24 is replaced by one first four-way valve 41. Also, the pair of the third three-way valve 25 and the first shut-off valve 29 is replaced by one second four-way valve 42. Other configurations are the same as those in the first embodiment. The first four-way valve 41 and the second four-way valve 42 are controlled by the control circuit described in the first embodiment.

[0085] The first four-way valve 41 includes a port for receiving the cooling water flowing out from the chiller 14 and discharging the received cooling water to the radiator 31 side, a port for discharging it to the cooler core 32 side, and a port for discharging it to the battery heat exchanger 34 side.

[0086] With this first four-way valve 41, a cooling water flow path configuration similar to that realized by the first three-way valve 23 and the second three-way valve 24 in the first embodiment is realized. In fact, in the hot water utilization mode, the ports on the cooler core 32 side and the ports on the battery heat exchanger 34 side are closed, and the port on the radiator 31 side is opened so that the cooling water flowing into the first four-way valve 41 from the chiller 14 flows to the radiator 31 side. Also, in the cold water utilization mode, the port on the radiator 31 side is closed, and the other ports are opened so that the cooling water flowing into the first four-way valve 41 from the chiller 14 flows to the cooler core 32 and the battery heat exchanger 34.

[0087] In addition, as a variation of the hot water utilization mode, when the cooling water from the chiller 14 is made to flow through the battery heat exchanger 34 to cool the battery BT, the port on the battery heat exchanger 34 side of the first four-way valve 41 is also opened. Also, as a variation of the cold water utilization mode, when the cooling water from the chiller 14 is not made to flow through the battery heat exchanger 34, the port on the battery heat exchanger 34 side of the first four-way valve 41 is closed. Also, when the cooling water from the chiller 14 is not made to flow through the cooler core 32, the port on the cooler core 32 side of the first four-way valve 41 is closed.

[0088] The second four-way valve 42 includes a port for receiving the cooling water flowing out from the water-cooled condenser 12 and discharging the received cooling water to the radiator 31 side, a port for discharging it to the heater core 33 side, and a port for discharging it to the battery heat exchanger 34 side.

[0089] With this second four-way valve 42, a flow path configuration of the cooling water similar to that realized by the third three-way valve 25 and the first shut-off valve 29 in the first embodiment is realized. In fact, in the hot water utilization mode, the port on the radiator 31 side is closed and the other ports are opened so that the cooling water flowing into the second four-way valve 42 from the water-cooled condenser 12 flows through the heater core 33 and the battery heat exchanger 34. Also, in the cold water utilization mode, the ports on the heater core 33 side and the battery heat exchanger 34 side are closed and the port on the radiator 31 side is opened so that the cooling water flowing into the second four-way valve 42 from the water-cooled condenser 12 flows to the radiator 31 side.

[0090] In addition, as a variation of the hot water utilization mode, when the cooling water from the water-cooled condenser 12 does not flow through the battery heat exchanger 34, the port of the second four-way valve 42 on the battery heat exchanger 34 side is closed. Also, when the cooling water from the water-cooled condenser 12 does not flow through the cooler core 32, the port of the second four-way valve 42 on the cooler core 32 side is closed. Further, as a variation of the cold water utilization mode, when the cooling water from the water-cooled condenser 12 flows through the battery heat exchanger 34 to warm the battery BT, the port of the second four-way valve 42 on the battery heat exchanger 34 side is also opened.

[0091] In this way, by using the first four-way valve 41 and the second four-way valve 42, the number of valves in the temperature control device 1 can be reduced. Note that changes such as those in this embodiment with respect to the first embodiment are also applicable to the second and third embodiments. Also, in this embodiment, the same effects as those in the first to third embodiments can be obtained from the same configurations.

[0092] In this embodiment, the first four-way valve 41, the sixth three-way valve 28, and the second shut-off valve 30 constitute a multi-switching mechanism that switches the path for guiding cooling water to the compressor flow path 20a in the cooling water flow path 20. And in the cold water circuit in the hot water utilization mode, the path from the first four-way valve 41 to the inflow side end of the compressor flow path 20a and the path from the outflow side end of the compressor flow path 20a to the radiator 31 are the first cooling path. And in the cold water circuit in the cold water utilization mode, the path from the sixth three-way valve 28 to the inflow side end of the compressor flow path 20a and the path from the outflow side end of the compressor flow path 20a to the chiller 14 are the second cooling path.

[0093] (Fifth Embodiment) Next, the fifth embodiment will be described with reference to FIG. 9. The temperature control device 1 of this embodiment is obtained by adding a third pump 51a, a fourth pump 51b, a first inverter 52a, a second inverter 52b, a first motor generator 53a, a second motor generator 53b, and an additional three-way valve 54 to the first embodiment. Also, a flow path for flowing cooling water through these added components is added.

[0094] Each of the third pump 51a and the fourth pump 51b is an electric pump that sucks and discharges cooling water, and is controlled by the control circuit described in the first embodiment. The suction sides of the third pump 51a and the fourth pump 51b are connected to the immediate upstream side of the battery heat exchanger 34 and the immediate downstream side of the radiator 31. And the third pump 51a discharges the sucked cooling water to the first inverter 52a and the first motor generator 53a side. Also, the fourth pump 51b discharges the sucked cooling water to the second inverter 52b and the second motor generator 53b side.

[0095] The first inverter 52a is a circuit that supplies the power supplied from the battery BT to the first motor generator 53a or accumulates the power in the battery BT by performing regenerative braking on the first motor generator 53a.

[0096] The first motor generator 53a outputs drive torque for the running of the vehicle by receiving power supply from the first inverter 52a, and is an electric motor that generates power for regeneration and outputs it to the first inverter 52a during regenerative braking.

[0097] The second inverter 52b is a circuit that supplies the power supplied from the battery BT to the second motor generator 53b, or accumulates power in the battery BT by performing regenerative braking on the second motor generator 53b.

[0098] The second motor generator 53b outputs drive torque for the running of the vehicle by receiving power supply from the second inverter 52b, and is an electric motor that generates power for regeneration and outputs it to the second inverter 52b during regenerative braking.

[0099] The first motor generator 53a and the second motor generator 53b operate complementarily under the control of a control device (not shown). Hereinafter, the first motor generator 53a, the second motor generator 53b, the first inverter 52a, and the second inverter 52b are collectively referred to as drive system devices.

[0100] The cooling water discharged from the third pump 51a exchanges heat with the first inverter 52a and the first motor generator 53a by passing through the flow paths provided therein, and then flows into the additional three-way valve 54. The cooling water discharged from the fourth pump 51b exchanges heat with the second inverter 52b and the second motor generator 53b by passing through the flow paths provided therein, and then flows into the additional three-way valve 54.

[0101] The additional three-way valve 54 has a port for receiving the cooling water flowing in from the drive system device side and discharging the received cooling water to the radiator 31 side, and a port for discharging it to the downstream side of the battery heat exchanger 34 and the upstream side of the fifth three-way valve 27, and is controlled by the control circuit shown in the first embodiment.

[0102] The operation of this embodiment will be described below. In this embodiment, while the operation of the first embodiment is being performed, cooling water may circulate between the radiator 31 and the drive system equipment. To achieve this, the third pump 51a and the fourth pump 51b operate under the control of the control circuit. Further, in this case, under the control of the control circuit, in the additional three-way valve 54, the port on the radiator 31 side opens and the port on the downstream side of the battery heat exchanger 34 closes.

[0103] As a result, cooling water circulates between the radiator 31 and the drive system equipment, and the heat given to the cooling water by the heat exchange between the drive system equipment and the cooling water is released to the outside by the radiator 31. That is, the drive system equipment is cooled. Note that such circulation of the cooling water between the radiator 31 and the drive system equipment is performed, for example, in the cold water utilization mode, but it may also be performed in other modes.

[0104] Also, in this embodiment, while the operation of the first embodiment is being performed, cooling water may flow through the drive system equipment in the same manner as the battery heat exchanger 34. To achieve this, the third pump 51a and the fourth pump 51b operate under the control of the control circuit. Further, in this case, under the control of the control circuit, in the additional three-way valve 54, the port on the downstream side of the battery heat exchanger 34 opens and the port on the radiator 31 side closes.

[0105] As a result, cooling water flows in parallel through the drive system equipment and the battery heat exchanger 34. Therefore, the drive system equipment is heated or cooled in the same manner as the battery BT. Note that heating or cooling the drive system equipment in the same manner as the battery BT may be performed in either the cold water utilization mode or the warm water utilization mode.

[0106] Note that changes such as this embodiment with respect to the first embodiment are also applicable to the second to fourth embodiments. Also, in this embodiment, the same effects as those of the first to fourth embodiments can be obtained from the same configurations.

[0107] (Sixth Embodiment) Next, the sixth embodiment will be described with reference to FIG. 10. The temperature control device 1 of this embodiment has an additional radiator 55 and a flow path for flowing cooling water added thereto, as compared with the fifth embodiment. Other configurations are the same as those of the fifth embodiment.

[0108] The additional radiator 55 is a heat exchanger that includes a flow path through which cooling water circulates and exchanges heat between an external heat medium AA such as air outside the vehicle compartment and the cooling water. In this embodiment, the connection destinations on the suction sides of the third pump 51a and the fourth pump 51b are on the downstream side of the additional radiator 55, instead of on the downstream side of the radiator 31 in the fifth embodiment.

[0109] Further, the additional three-way valve 54 has a port connected to the upstream side of the additional radiator 55, instead of the port connected to the upstream side of the radiator 31 in the fifth embodiment, as a port other than the port on the battery heat exchanger 34 side.

[0110] In the operation of this embodiment, instead of the cooling water circulating between the radiator 31 and the drive system equipment in the fifth embodiment, the cooling water circulates between the additional radiator 55 and the drive system equipment. Other operations are the same as those of the fifth embodiment. In this embodiment, the same effects can be obtained from the same configurations as those in the fifth embodiment.

[0111] (Seventh Embodiment) Next, the seventh embodiment will be described with reference to FIGS. 11 to 16. The temperature control device 1 of this embodiment has a compression unit 100 including a compression mechanism 11a and a motor 11b of the compressor 11 in the first embodiment. Hereinafter, the configuration of this compression unit 100 will be described.

[0112] FIG. 11 is an axial cross-sectional view of the compression unit 100 cut along the axis CL of the rotating shaft 170. Hereinafter, the direction extending along the axis CL of the rotating shaft 170 of the compression unit 100 is defined as the axial direction DRa.

[0113] The housing 120 has, in addition to the main housing 121 and the sub-housing 122 disposed at both ends in the axial direction DRa, a first middle housing 123, a second middle housing 124, and a third middle housing 125 disposed between the two. The housing 120 has a sealed container structure in which the main housing 121, the sub-housing 122, the first middle housing 123, the second middle housing 124, and the third middle housing 125 are hermetically fastened by fastening members such as bolts (not shown).

[0114] The main housing 121 is disposed on one side in the axial direction DRa. The main housing 121 has a bottomed cylindrical shape with an opening on the other side in the axial direction DRa. A refrigerant suction port 182 is formed at the bottom on one side in the axial direction DRa in the main housing 121. Inside the main housing 121, the motor 11b described in the first embodiment is accommodated.

[0115] The sub-housing 122 is disposed on the other side in the axial direction DRa. That is, the sub-housing 122 is disposed on the side opposite to the main housing 121 with respect to the compression mechanism 11a described in the first embodiment. The sub-housing 122 has a plate shape. A refrigerant discharge port 181 is formed in the sub-housing 122.

[0116] The first middle housing 123 is disposed adjacent to the main housing 121 so as to cover the entire opening of the main housing 121. The rotation shaft 170 penetrates through a substantially central portion of the first middle housing 123. As shown in FIG. 16, a second space 832 communicating with the refrigerant suction port 182 is formed in the first middle housing 123.

[0117] The second middle housing 124 is disposed between the sub-housing 122 and the third middle housing 125. A through hole through which the rotating shaft 170 penetrates is formed in a substantially central portion of the second middle housing 124. As shown in FIGS. 11 and 14, a first space 831 communicating with the refrigerant discharge port 181 is formed in the second middle housing 124. As shown in FIG. 15, a refrigerant lead-out hole 830 that communicates with the first space 831 at one end and communicates with a discharge port 421 (to be described later) at the other end is formed in the second middle housing 124.

[0118] The third middle housing 125 is disposed between the first middle housing 123 and the second middle housing 124. A through hole for accommodating the compression mechanism 11a is formed in a substantially central portion of the third middle housing 125.

[0119] The motor 11b has a stator 131 and a rotor 132. When the stator 131 is energized, a magnetic force is generated in the stator 131, and the rotor 132 rotates by the magnetic force. The rotation of the rotor 132 is transmitted to the rotating shaft 170, so that the rotating shaft 170 rotates.

[0120] The rotating shaft 170 is accommodated in the housing 120 and is rotatably supported. The rotating shaft 170 is composed of a columnar main shaft 171 centered on the axis CL and a crank portion 172 provided in the middle of the axial direction DRa of the main shaft 171 and eccentric with respect to the axis CL. The crank portion 172 is disposed in the through hole of the third middle housing 125. An oil supply passage 174 for supplying oil to the sliding portion of the compression mechanism 11a is formed in the rotating shaft 170.

[0121] The compression mechanism 11a is disposed between the first space 831 and the second space 832 so as to be aligned with the first space 831 and the second space 832 in the axial direction DRa of the rotating shaft 170. As shown in FIGS. 11 to 16, the compression mechanism 11a has a crank portion 172, a piston rotor 141, a vane 143, and a spring 144. The compression mechanism 11a has a rolling piston type structure in which the compression chamber 423 is separated into a high pressure and a low pressure by a vane 143 installed on the side of the third middle housing 125 corresponding to the cylinder.

[0122] The piston rotor 141 functions as a rolling piston. The piston rotor 141 is fitted on the outer periphery of the crank portion 172. Similar to the crank portion 172, the central axis of the piston rotor 141 is eccentric with respect to the axis CL of the rotating shaft 170. The piston rotor 141 receives the rotation of the rotating shaft 170 and performs a revolution motion with respect to the inner peripheral surface of the third middle housing 125. The piston rotor 141 corresponds to a movable member.

[0123] A compression chamber 423 for compressing the refrigerant is formed between the outer peripheral surface of the piston rotor 141 and the inner peripheral surface of the third middle housing 125. The compression chamber 423 is partitioned by the piston rotor 141, the third middle housing 125, the first middle housing 123, and the second middle housing 124.

[0124] As shown in FIG. 13, a discharge port 421 that extends in the axial direction DRa and communicates the compression chamber 423 with the refrigerant discharge hole 830 is formed in the third middle housing 125. Further, as shown in FIG. 12, a suction port 422 that extends in the axial direction DRa and communicates the compression chamber 423 with the second space 832 is formed in the third middle housing 125. The discharge port 421 and the suction port 422 are formed at different circumferential positions centered on the axis CL in the third middle housing 125 so as not to communicate with each other.

[0125] The discharge port 421 and the suction port 422 are closed by the outer peripheral surface of the piston rotor 141 when the piston rotor 141 is located at the top dead center, and are opened when the piston rotor 141 is at a position deviated from the top dead center. As shown in FIGS. 12 and 13, a vane groove for slidably receiving the vane 143 is formed in the third middle housing 125.

[0126] In the third middle housing 125, a pressure chamber 425 is defined by the inner wall of the vane groove and the rear end surface of the vane 143 (i.e., the radially outer surface centered on the axis CL). The spring 144 is disposed in the pressure chamber 425 to bias the front end surface of the vane 143 toward the piston rotor 141.

[0127] As shown in FIGS. 14 and 15, a back pressure introduction hole 841 for communicating the pressure chamber 425 with the first space 831 is formed in the second middle housing 124. Thereby, high pressure generated by the compression mechanism 11a is introduced into the pressure chamber 425 from the back pressure introduction hole 841. Thereby, in addition to the biasing force by the spring 144, the vane 143 is biased toward the piston rotor 141 by the pressure in the pressure chamber 425.

[0128] The vane 143 is a partitioning member that partitions the compression chamber 423 in the circumferential direction centered on the axis CL. The vane 143 presses the piston rotor 141 by the biasing force of the spring 144 and the pressure in the pressure chamber 425. The vane 143 is accommodated in the vane groove 424 and is displaceable in a direction approaching the axis CL of the rotating shaft 170 and a direction away from the axis CL. The vane 143 is displaced to the position farthest from the axis CL when the piston rotor 141 is located at the top dead center, and is displaced to the position closest to the axis CL when the piston rotor 141 is located at the bottom dead center. As shown in FIG. 14, a discharge valve 531 for preventing the flow of refrigerant (i.e., backflow) from the first space 831 to the compression chamber 423 is formed in the first space 831.

[0129] The operation of the compression unit 100 as described above will be explained below. When the motor 11b is energized during the operation of the compression unit 100, the rotating shaft 170 rotates, and together with it, the piston rotor 141 also rotates eccentrically.

[0130] Due to the rotation of this piston rotor 141, the refrigerant evaporated in the chiller 14 is inhaled from the refrigerant suction port 182, through the second space 832, and from the suction port 422 into the compression chamber 423. The refrigerant inhaled into the compression chamber 423 moves in the circumferential direction around the axis CL while being compressed as the piston rotor 141 rotates. The refrigerant that has been compressed to a high temperature and high pressure is discharged from the discharge port 421 through the refrigerant outlet hole 830 into the first space 831. Then, the refrigerant discharged into the first space 831 is discharged from the refrigerant discharge port 181 to the water-cooled condenser 12 side outside the compression unit 100.

[0131] The flow path of the cooling water flowing through the compression unit 100 will be explained below. As shown in FIG. 11, a compressor flow path 20a is formed in the first middle housing 123, the second middle housing 124, and the third middle housing 125. The compressor flow path 20a of the present embodiment passes through the inside of the compression unit 100 among the cooling water flow paths 20. The compressor flow path 20a has an inflow portion 851 that allows cooling water to flow in from other parts of the cooling water flow path 20, an outflow portion 852 that allows cooling water to flow out to other parts of the cooling water flow path 20, and a heat exchange passage 853 that connects the inflow portion 851 and the outflow portion 852.

[0132] The inflow portion 851 is a flow path that receives the cooling water flowing into the compression unit 100 from the part of the cooling water flow path 20 outside the compression unit 100. The inflow portion 851 is formed in the second middle housing 124 and has a port portion 851a and an enclosing portion 851b.

[0133] As shown in FIGS. 11, 14, and 15, one end of the port portion 851a opens to the outer peripheral surface of the second middle housing 124 and communicates with a portion of the cooling water flow path 20 other than the compressor flow path 20a. Further, the port portion 851a extends from the one end to the other end inward in the radial direction about the axis CL within the second middle housing 124. The other end of the port portion 851a communicates with the surrounding portion 851b on the side of the third middle housing 125.

[0134] As shown in FIGS. 11 and 15, the surrounding portion 851b is disposed between the port portion 851a and the third middle housing 125, extends in the circumferential direction surrounding the axis CL, and communicates with the port portion 851a at the central portion in its longitudinal direction and opens to the side of the third middle housing 125 throughout its longitudinal direction.

[0135] The outflow portion 852 is a flow path for discharging cooling water from the portion inside the compression unit 100 of the cooling water flow path 20 to the outside of the compression unit 100. The outflow portion 852 is formed in the first middle housing 123 and has a port portion 852a and a surrounding portion 852b.

[0136] As shown in FIGS. 11 and 16, one end of the port portion 852a opens to the outer peripheral surface of the first middle housing 123 and communicates with a portion of the cooling water flow path 20 other than the compressor flow path 20a. Further, the port portion 852a extends from the one end to the other end inward in the radial direction about the axis CL within the first middle housing 123. The other end of the port portion 852a communicates with the surrounding portion 852b on the side of the third middle housing 125.

[0137] As shown in FIGS. 11 and 16, the surrounding portion 852b is disposed between the port portion 852a and the third middle housing 125, extends in the circumferential direction surrounding the axis CL, and communicates with the port portion 852a at the central portion in its longitudinal direction and opens to the side of the third middle housing 125 throughout its longitudinal direction.

[0138] As shown in FIGS. 11, 12, and 13, the heat exchange passage 853 is formed in the third middle housing 125. The heat exchange passage 853 has a plurality of sub-channels. In the examples of FIGS. 12 and 13, the number of sub-channels is 11, but it is not limited to this number.

[0139] Each of the sub-channels communicates with the surrounding portion 851b of the inflow portion 851 at one end thereof, extends along the axis CL from one end to the other end, and communicates with the surrounding portion 852b of the outflow portion 852 at the other end. That is, these sub-channels flow the cooling water supplied from the same surrounding portion 851b in parallel and send it to the same surrounding portion 852b.

[0140] These sub-channels are dispersedly arranged in the circumferential direction centered on the axis CL in the third middle housing 125 so as to surround the compression chamber 423. And the surface areas of the sub-channels in the third middle housing 125 are all the same.

[0141] When the third middle housing 125 is divided into two parts, a part closer to the discharge port 421 and a part closer to the suction port 422, the number of sub-channels per unit volume of the third middle housing 125 is larger in the part closer to the discharge port 421 than in the part closer to the suction port 422. Therefore, the surface area of the heat exchange passage 853 per unit volume of the third middle housing 125 is larger in the part closer to the discharge port 421 than in the part closer to the suction port 422.

[0142] In the third middle housing 125, the larger the surface area of the flow path through which the cooling water flows, the larger the amount of heat exchange between the cooling water and the third middle housing 125. And in the compression chamber 423, the compression progresses and the refrigerant becomes high-pressure and high-temperature as it approaches the discharge port 421 from the suction port 422. Therefore, as described above, when the side closer to the discharge port 421 has a larger surface area of the heat exchange passage per unit volume, the cooling efficiency becomes higher.

[0143] In the compression chamber 423, the refrigerant sucked from the suction port 422 is gradually compressed while advancing from the suction port 422 to the discharge port 421 in the circumferential direction (i.e., clockwise in FIG. 12 and counterclockwise in FIG. 13) around the axis CL within the compression chamber 423. This is because the piston rotor 141 rotates in the clockwise direction in FIG. 12 and the counterclockwise direction in FIG. 13.

[0144] Therefore, as shown in FIGS. 12 and 13, the number density of the sub-flow paths in the third middle housing 125 is also gradually increased from the suction port 422 to the discharge port 421 in the circumferential direction around the axis CL within the compression chamber 423, thereby increasing the cooling efficiency. That is, the surface area of the heat exchange passage 853 per unit volume of the third middle housing 125 is gradually increased from the suction port 422 to the discharge port 421 in the circumferential direction around the axis CL within the compression chamber 423 in the direction of rotation of the piston rotor 141, thereby increasing the cooling efficiency.

[0145] For example, with the axis CL as the center, the direction from the axis CL to the vane 143 being 0°, and the direction of rotation of the piston rotor 141 being positive, the range from 0° to less than 90° is defined as the first quadrant, and the range from 90° to less than 180° is defined as the second quadrant. Also, the range from 180° to less than 270° is defined as the third quadrant, and the range from 270° to less than 360° is defined as the fourth quadrant.

[0146] In this case, if the surface areas of the heat exchange passage 853 per unit volume of the third middle housing 125 in the first, second, third, and fourth quadrants are S1, S2, S3, and S4 respectively, then S1 < S2 < S3 < S4.

[0147] During the operation of the compression unit 100, the cooling water flows through the compressor flow path 20a configured as described above as shown by the dashed line in FIG. 11. For example, in the hot water utilization mode of FIG. 2, the cooling water flowing out from the first three-way valve 23 flows into the inflow portion 851, further flows through the heat exchange passage 853 and the outflow portion 852 in this order, then flows out of the compressor flow path 20a from the outflow portion 852, and further flows into the second shut-off valve 30.

[0148] As a result, the compression mechanism 11a including the compression chamber 423 can be cooled by the chilled water passing through the heat exchange passage 853. That is, the compression mechanism 11a can be cooled using the cooling heat before being discarded by the radiator 31.

[0149] Also, for example, in the chilled water utilization mode of FIG. 3, the cooling water flowing out from the sixth three-way valve 28 flows into the inflow portion 851, further flows through the heat exchange passage 853 and the outflow portion 852 in this order, then flows out of the compressor flow path 20a from the outflow portion 852, and further flows into the radiator 31.

[0150] As a result, the compression mechanism 11a including the compression chamber 423 can be cooled by the chilled water passing through the heat exchange passage 853. That is, the compression mechanism 11a can be cooled using the chilled water after being used in the utilization-side heat exchanger.

[0151] (1) As described above, the compressor flow path 20a has the heat exchange passage 853 formed inside the third middle housing 125. By being configured in this way, effective heat exchange can be performed on the compression chamber that may require cooling or heating. Therefore, the cooling efficiency of the compressor can be enhanced.

[0152] (2) Also, let the surface area of the heat exchange passage 853 per unit volume in the portion of the third middle housing 125 closer to the discharge port 421 than the suction port 422 be SX1. And let the surface area of the heat exchange passage 853 per unit volume in the portion of the third middle housing 125 closer to the suction port 422 than the discharge port 421 be SX2. In that case, SX1 is larger than SX2.

[0153] In the compression chamber 423, the compression progresses as the refrigerant approaches the discharge port 421 from the suction port 422, and it becomes high-pressure and high-temperature. Therefore, the temperature of the third middle housing 125 is higher on the side closer to the discharge port 421. Therefore, as described above, when the surface area of the heat exchange passage 853 per unit volume is larger on the side closer to the discharge port 421, the cooling efficiency of the compression mechanism 11a is increased.

[0154] Note that the compression unit 100 configured as in the present embodiment is also applicable to the second to sixth embodiments. Further, in the present embodiment, the same effects as those of the first to sixth embodiments can be obtained from the same configurations.

[0155] (Eighth Embodiment) Next, the eighth embodiment will be described with reference to FIG. 17. In this embodiment, the configuration of the heat exchange passage 853 is changed with respect to the seventh embodiment. Other configurations are the same as those of the seventh embodiment.

[0156] Specifically, as shown in FIG. 17, the heat exchange passage 853 has seven sub-channels. However, it is not limited to seven, and it may be more or less than seven. Similar to the seventh embodiment, each of the sub-channels is formed in the third middle housing 125, communicates with the surrounding portion 851b at one end thereof, extends along the axis CL from one end to the other end, and communicates with the surrounding portion 852b at the other end.

[0157] And the number density of the sub-channels in the third middle housing 125 is substantially the same in the circumferential direction around the axis CL in the compression chamber 423. And the surface areas of the sub-channels are not the same, and gradually increase in the circumferential direction around the axis CL in the compression chamber 423 in the rotational direction of the piston rotor 141 from the suction port 422 to the discharge port 421. This is achieved by gradually increasing the sizes of the sub-channels in the radial direction and the circumferential direction centered on the axis CL along the circumferential direction in the rotational direction of the piston rotor 141 from the suction port 422 to the discharge port 421.

[0158] By doing so as well, similar to the seventh embodiment, the surface area of the heat exchange passage 853 per unit volume of the third middle housing 125 can be gradually increased from the suction port 422 to the discharge port 421 in the circumferential direction. Specifically, SX1 is larger than SX2. Also, S1 < S2 < S3 < S4 holds.

[0159] Other configurations and operations of this embodiment are the same as those of the seventh embodiment. And in this embodiment as well, the same effects as those of the seventh embodiment can be obtained.

[0160] (Ninth Embodiment) Next, the ninth embodiment will be described with reference to FIG. 18. In this embodiment, the configuration of the heat exchange passage 853 is changed with respect to the seventh embodiment. Other configurations are the same as those of the seventh embodiment.

[0161] Specifically, as shown in FIG. 18, the heat exchange passage 853 has five sub-channels. However, it is not limited to five, and it may be more or less than five. Similar to the seventh embodiment, each of the sub-channels is formed in the third middle housing 125, communicates with the surrounding portion 851b at one end thereof, extends along the axis CL from one end to the other end, and communicates with the surrounding portion 852b at the other end.

[0162] And the number density of the sub-channels in the third middle housing 125 is generally the same in the circumferential direction centered on the axis CL in the compression chamber 423. And the surface area of the sub-channels gradually increases in the circumferential direction centered on the axis CL in the compression chamber 423 from the suction port 422 to the discharge port 421 in the rotational direction of the piston rotor 141. This is achieved by making the sizes of the sub-channels in the radial direction centered on the axis CL the same and gradually increasing the sizes of the sub-channels in the circumferential direction along the circumferential direction from the suction port 422 to the discharge port 421 in the rotational direction of the piston rotor 141.

[0163] By doing so as well, similar to the seventh embodiment, the surface area of the heat exchange passage 853 per unit volume of the third middle housing 125 can be gradually increased in the circumferential direction from the suction port 422 to the discharge port 421 in the rotational direction of the piston rotor 141. Specifically, SX1 is larger than SX2. Also, S1 < S2 < S3 < S4 holds.

[0164] Other configurations and operations of this embodiment are the same as those of the seventh embodiment. And in this embodiment as well, the same effects as those of the seventh embodiment can be obtained.

[0165] (Tenth Embodiment) Next, the tenth embodiment will be described with reference to FIG. 19. In this embodiment, the configuration of the heat exchange passage 853 is changed with respect to the seventh embodiment. Other configurations are the same as those of the seventh embodiment.

[0166] Specifically, as shown in FIG. 19, the heat exchange passage 853 has eight sub-channels. However, it is not limited to eight, and it may be more or less than eight. Similar to the seventh embodiment, each of the sub-channels is formed in the third middle housing 125, communicates with the surrounding portion 851b at one end, extends along the axis CL from one end to the other end, and communicates with the surrounding portion 852b at the other end.

[0167] And the number density of the sub-channels in the third middle housing 125 is generally the same in the circumferential direction around the axis CL in the compression chamber 423. And the surface area of the sub-channels gradually increases in the circumferential direction around the axis CL in the compression chamber 423 from the suction port 422 to the discharge port 421 in the rotational direction of the piston rotor 141. This is achieved by making the sizes of the sub-channels in the circumferential direction around the axis CL the same while gradually increasing the sizes of the sub-channels in the radial direction around the axis CL along the circumferential direction from the suction port 422 to the discharge port 421.

[0168] By doing so, similar to the seventh embodiment, the surface area of the heat exchange passage 853 per unit volume of the third middle housing 125 can be gradually increased in the circumferential direction from the suction port 422 to the discharge port 421 in the rotational direction of the piston rotor 141. Specifically, SX1 is larger than SX2. Also, S1 < S2 < S3 < S4 holds.

[0169] Other configurations and operations of this embodiment are the same as those of the seventh embodiment. And in this embodiment as well, the same effects as those of the seventh embodiment can be obtained.

[0170] (Eleventh Embodiment) Next, the eleventh embodiment will be described with reference to FIG. 20. In this embodiment, the configuration of the heat exchange passage 853 is changed with respect to the seventh embodiment. Other configurations are the same as those of the seventh embodiment.

[0171] Specifically, as shown in FIG. 20, the heat exchange passage 853 is a single passage. The heat exchange passage 853 is formed in the third middle housing 125, communicates with the surrounding portion 851b at one end thereof, extends along the axis CL from one end to the other end, and communicates with the surrounding portion 852b at the other end.

[0172] Also, the heat exchange passage 853 is formed in the third middle housing 125 in such a shape that the third middle housing 125 is composed of an inner peripheral portion 125a, an outer peripheral portion 125b, and a plurality of protruding portions 125c.

[0173] The inner peripheral portion 125a has a cylindrical shape centered on the axis CL. The compression chamber 423 is partitioned by the inner peripheral surface of the inner peripheral portion 125a and the outer peripheral surface of the piston rotor 141. The outer peripheral surface of the inner peripheral portion 125a faces the heat exchange passage 853 and is connected to the plurality of protruding portions 125c.

[0174] The outer peripheral portion 125b houses the inner peripheral portion 125a and the protruding portions 125c therein and forms the outer shell of the third middle housing 125. The inner peripheral portion 125a side of the outer peripheral portion 125b is connected to the inner peripheral portion 125a in the vicinity of the vane 143 and faces the inner peripheral portion 125a across the heat exchange passage 853 in other portions.

[0175] Each of the protruding portions 125c extends radially outward from the surface of the inner peripheral portion 125a on the outer peripheral portion 125b side about the axis CL. The protruding portions 125c are respectively arranged at different positions in the circumferential direction about the axis CL. Therefore, the protruding portions 125c extend radially as a whole.

[0176] The number density of the protruding portions 125c gradually increases in the circumferential direction about the axis CL in the compression chamber 423 in the rotational direction of the piston rotor 141 from the suction port 422 to the discharge port 421. Thereby, the surface area of the heat exchange passage 853 gradually increases in the circumferential direction in the rotational direction of the piston rotor 141 from the suction port 422 to the discharge port 421. Thereby, the cooling efficiency increases.

[0177] By doing so, as in the seventh embodiment, the surface area of the heat exchange passage 853 can be gradually increased in the circumferential direction from the suction port 422 to the discharge port 421. Specifically, SX1 is larger than SX2. Also, S1 < S2 < S3 < S4 holds.

[0178] Other configurations and operations of this embodiment are the same as those of the seventh embodiment. And in this embodiment, the same effects as those of the seventh embodiment can be obtained.

[0179] (12th Embodiment) Next, the 12th embodiment will be described with reference to FIG. 21. In this embodiment, the configuration of the compressor flow path 20a is changed with respect to the 1st embodiment. Specifically, the compressor flow path 20a of this embodiment has a plurality of sub-flow paths configured in parallel. And, an adjustment unit 11d for adjusting the flow rate of the sub-flow path is provided in some or all of these plurality of sub-flow paths. Other configurations are the same as those of the 1st embodiment.

[0180] Each sub-flow path is arranged in the vicinity of the compression mechanism 11a. Therefore, the cooling water flowing through each sub-flow path can exchange heat with the compression mechanism 11a. The cooling water that enters the compressor flow path 20a branches and flows into these sub-flow paths, exchanges heat with the compression mechanism 11a in each sub-flow path, and then merges and flows out of the compressor flow path 20a.

[0181] Each of the adjustment units 11d may be, for example, a throttle that reduces the flow path cross-sectional area with respect to the front and rear flow paths. Alternatively, each of the adjustment units 11d may be a flow rate adjustment valve. The flow rate of the sub-flow path adjusted by each of the adjustment units 11d may be controllable by the control circuit described in the 1st embodiment. Alternatively, the flow rate of the sub-flow path adjusted by each of the adjustment units 11d may be fixedly determined in advance.

[0182] During the manufacture of the compressor 11, by adjusting the flow rate using the adjustment unit 11d, the flow rate of the cooling water can be adjusted for each sub-flow path without adjusting the flow path cross-sectional area of the sub-flow path. For example, the flow rate of the cooling water can be made different for each sub-flow path.

[0183] For example, it is also possible to apply the compressor flow path 20a configured as in this embodiment to the compression unit 100 of the 7th embodiment. In that case, the sub-flow path of this embodiment corresponds to the sub-flow path that constitutes the heat exchange passage 853 formed inside the third middle housing 125.

[0184] Then, let the flow rate of the heat exchange passage 853 per unit volume in the portion of the third middle housing 125 closer to the discharge port 421 than the suction port 422 be FX1. And let the flow rate of the heat exchange passage 853 per unit volume in the portion of the third middle housing 125 closer to the suction port 422 than the discharge port 421 be FX2. In this case, the adjustment unit 11d can be adjusted so that FX1 is larger than FX2.

[0185] (1) As described above, the compressor flow path 20a has a plurality of sub-flow paths arranged in parallel and an adjustment unit 11d that adjusts the flow rate of at least some of the plurality of sub-flow paths. By doing so, the inside of the compressor 11 can be efficiently cooled.

[0186] (The 13th Embodiment) Next, the 13th embodiment will be described with reference to FIG. 22. In this embodiment, the path of the compressor flow path 20a inside the compressor 11 is different from that of the first embodiment. Other configurations are the same as those of the first embodiment.

[0187] Specifically, the compressor flow path 20a of the present embodiment includes a flow path that passes near the compression mechanism 11a and exchanges heat between the compression mechanism 11a and the cooling water, and a flow path that passes near the motor 11b and exchanges heat between the motor 11b and the cooling water. Note that the flow path passing near the compression mechanism 11a and the flow path passing near the motor 11b may be configured in parallel or in series.

[0188] Other configurations are the same as those of the first embodiment. Also, in the flow path outside the compressor flow path 20a in the cooling water flow path 20, the path through which the cooling water flows in the cold water utilization mode and the hot water utilization mode is the same as that of the first embodiment.

[0189] Thereby, in both the cold water utilization mode and the hot water utilization mode, the cooling water flowing into the compressor 11 cools or heats the compression mechanism 11a and the motor 11b in the compressor 11.

[0190] (1) Thus, the compressor flow path includes a flow path for heat-exchanging the inverter circuit 11c and the cooling water. By doing so, the motor 11b, which has a large heat generation amount and is easily affected by heat, can be effectively cooled.

[0191] Note that the modifications such as those in the present embodiment with respect to the first embodiment are also applicable to the second to twelfth embodiments. Also, in the present embodiment, the same effects can be obtained from the same configurations as those in the first to twelfth embodiments.

[0192] (The Fourteenth Embodiment) Next, the fourteenth embodiment will be described with reference to FIGS. 23, 24, and 25. In the temperature control device 1 of the present embodiment, the configuration of the cooling water flow path 20 is partially changed with respect to the first embodiment. Specifically, as shown in FIG. 23, the sixth three-way valve 28 of the first embodiment is abolished, and the discharge side of the second pump 22 is directly connected to the chiller 14. Also, the second shut-off valve 30 of the first embodiment is abolished, and the flow path where the second shut-off valve 30 was arranged, that is, the flow path connecting the outlet side of the compressor flow path 20a and the discharge side of the second pump 22, is also abolished.

[0193] Also, the flow path on the radiator 31 side of the first three-way valve 23 is connected to the radiator 31 via the compressor flow path 20a in the first embodiment, but in the present embodiment, it is connected to the radiator 31 bypassing the compressor flow path 20a.

[0194] Also, an additional three-way valve 61 is arranged between the first pump 21 and the water-cooled condenser 12. The additional three-way valve 61 is a three-way valve that switches the presence or absence of the flow of the cooling water sent from the first pump 21 to the water-cooled condenser 12 side and the presence or absence of the flow to the inlet side end of the compressor flow path 20a. The operation of the additional three-way valve 61 is controlled by the control circuit described in the first embodiment.

[0195] Also, a flow path is provided from the outflow side end of the compressor flow path 20a to the downstream of the additional three-way valve 61 and upstream of the water-cooled condenser 12. Other configurations are the same as those in the first embodiment.

[0196] Next, the operation of this embodiment will be described. As shown in FIG. 24, in the hot water utilization mode, the additional three-way valve 61 blocks the port on the compressor flow path 20a side and opens the port on the water-cooled condenser 12 side. As a result, the cooling water flowing out from the first pump 21 does not flow into the compressor flow path 20a but flows into the water-cooled condenser 12. The opening and closing states of the other valves and the operating states of the compressor 11, pumps 21, and 22 are the same as those in the hot water utilization mode of the first embodiment.

[0197] At this time, the hot water circuit in which the cooling water is heated by the water-cooled condenser 12 circulates in the same path as in the first embodiment, except that the cooling water flowing out from the first pump 21 and flowing into the water-cooled condenser 12 passes through the additional three-way valve 61. Thus, hot water is supplied to the utilization side as in the first embodiment.

[0198] Also, regarding the circulation path of the cold water circuit in which the cooling water is cooled by the chiller 14, it is the same as that in the hot water utilization mode of the first embodiment, except that it bypasses the compressor flow path 20a before flowing out of the first three-way valve 23 and flowing into the radiator 31. That is, the cooling water circulates in the order of the chiller 14, the first three-way valve 23, the radiator 31, the fourth three-way valve 26, the second pump 22, and the chiller 14. As a result, the cold heat is discarded to the external heat medium AA by the radiator 31. In this way, in the hot water utilization mode of this embodiment, the cooling water does not flow through the compressor flow path 20a.

[0199] Also, as shown in FIG. 25, in the cold water utilization mode, the additional three-way valve 61 has the port on the compressor flow path 20a side opened and the port on the water-cooled condenser 12 side blocked. As a result, the cooling water flowing out from the first pump 21 flows through the additional three-way valve 61 and the compressor flow path 20a, and then flows into the water-cooled condenser 12. The opening and closing states of the other valves and the operating states of the compressor 11, pumps 21, and 22 are the same as those in the cold water utilization mode of the first embodiment.

[0200] At this time, the cold water circuit in which the cooling water is cooled by the chiller 14 is the same as the cold water utilization mode of the first embodiment, except that the cooling water flowing out from the second pump 22 bypasses the compressor flow path 20a before flowing into the chiller 14. Thus, as in the first embodiment, cold water is supplied to the utilization side.

[0201] Also at this time, regarding the circulation path of the hot water circuit in which the cooling water is heated by the water-cooled condenser 12, it is the same as the cold water utilization mode of the first embodiment, except that the cooling water flowing out from the first pump 21 flows into the water-cooled condenser 12 after flowing through the compressor flow path 20a from the additional three-way valve 61. That is, the cooling water circulates in the order of the water-cooled condenser 12, the third three-way valve 25, the radiator 31, the fourth three-way valve 26, the first pump 21, the additional three-way valve 61, the compressor flow path 20a, and the water-cooled condenser 12.

[0202] As a result, in the cold water utilization mode, the cooling water that has been radiated by the radiator 31 and has its temperature reduced is cooled by the compressor flow path 20a to the compressor mechanism 11a of the compressor 11 before being heated by the water-cooled condenser 12.

[0203] When the compressor 11 is operating, the temperature of the compressor 11 often becomes higher than the temperature of the cooling water heated by the chiller 14. Also, in many cases, to cool the compressor 11, not the cold water in the colder cold water circuit but the hot water in the hot water circuit is sufficient.

[0204] In such a case, instead of using the chilled water in the chilled water circuit, by cooling the compressor 11 with the warm water in the warm water circuit, it is possible to cool the compressor 11 while suppressing the possibility of interfering with the effect of cooling the utilization side.

[0205] (1) As described above, the cooling water flow path 20 of the present embodiment is configured such that the cooling water heated by the water-cooled condenser 12 flows through the compressor flow path 20a. In this way, instead of the cooling water cooled by the chiller 14, the cooling water heated by the water-cooled condenser 12 can be used for heat exchange with the compressor 11.

[0206] (2) Further, the cooling water flow path 20 is configured to cool the compressor 11 by the cooling water heated by the water-cooled condenser 12 flowing through the compressor flow path 20a. In this way, by cooling the compressor 11 with cooling water other than the cooling water cooled by the chiller 14, the cooling capacity of the chiller 14 can be used in a higher proportion for applications other than cooling the compressor 11 (for example, supply to the utilization side).

[0207] (3) Further, the cooling water flow path 20 is configured to cool the compressor 11 by the cooling water that has been heated by the water-cooled condenser 12, cooled by the radiator 31, and then flows through the compressor flow path 20a before being further heated by the water-cooled condenser 12. In this way, by using the cooling water that has been heated by the water-cooled condenser 12 and then cooled by the radiator 31, the compressor 11 can be efficiently cooled with relatively low-temperature warm water.

[0208] It should be noted that changes such as those in the present embodiment with respect to the first embodiment are also applicable to the third to thirteenth embodiments. Further, the same effects can be obtained from the same configurations as those in the present embodiment in the first to thirteenth embodiments.

[0209] (15th Embodiment) Next, the 15th embodiment will be described with reference to FIGS. 26, 27, 28, and 29. In the temperature control device 1 of this embodiment, the configuration of the cooling water flow path 20 is partially changed compared to the first embodiment. Specifically, in the first embodiment, the flow path on the radiator 31 side of the first three-way valve 23 is connected to the radiator 31 via the compressor flow path 20a, but in this embodiment, it bypasses the compressor flow path 20a and is connected to the radiator 31.

[0210] In addition, an additional three-way valve 61 is arranged between the first pump 21 and the water-cooled condenser 12. The additional three-way valve 61 is a three-way valve that switches the presence or absence of the flow of the cooling water sent from the first pump 21 to the water-cooled condenser 12 side and the presence or absence of the flow to the inflow side end of the compressor flow path 20a. The operation of the additional three-way valve 61 is controlled by the control circuit described in the first embodiment.

[0211] Also, a new flow path is formed from the outflow side end of the compressor flow path 20a to the flow path connecting the second shut-off valve 30 to the flow path connecting the additional three-way valve 61 and the water-cooled condenser 12, and a third shut-off valve 62 for switching the flow and blockage of the flow path is provided in the new flow path. The operation of the third shut-off valve 62 is controlled by the control circuit described in the first embodiment.

[0212] In addition, a heater 63 for heating the cooling water flowing through the flow path is provided in the flow path between the second pump 22 and the sixth three-way valve 28. The heater 63 is an electric heater that operates using electric power as an energy source. The operation of the heater 63 is controlled by the control circuit described in the first embodiment. Other configurations are the same as those in the first embodiment.

[0213] Next, the operation of this embodiment will be described. In this embodiment, the control circuit switches among three modes: a hot water utilization mode A, a hot water utilization mode B, and a cold water utilization mode. For example, the control circuit determines whether to execute the hot water utilization mode or the cold water utilization mode in the same manner as in the first embodiment. When it is determined to execute the small hot water mode, it further determines which of the hot water utilization modes A and B to execute. In this case, which of the hot water utilization modes A and B to execute may be determined based on, for example, the temperature outside the vehicle. For example, if the temperature outside the vehicle is equal to or higher than a threshold value (e.g., -10°C), the hot water utilization mode A may be executed, and if it is at an extremely low temperature below the threshold value, the hot water utilization mode B may be executed.

[0214] In the hot water utilization mode A, as shown in FIG. 27, the additional three-way valve 61 blocks the port on the compressor flow path 20a side and opens the port on the water-cooled condenser 12 side. Also, the third shut-off valve 62 is closed. Also, the heater 63 is turned off. The opening / closing states of the other valves and the operating states of the compressor 11, pumps 21, and 22 are the same as in the hot water utilization mode of the first embodiment.

[0215] At this time, in the hot water circuit where the cooling water is heated by the water-cooled condenser 12, the cooling water circulates in the same path as in the first embodiment, except that the cooling water that flows out of the first pump 21 and then flows into the water-cooled condenser 12 passes through the additional three-way valve 61. Thereby, hot water is supplied to the utilization side in the same manner as in the first embodiment.

[0216] Also at this time, the chilled water circuit in which the cooling water is cooled by the chiller 14 is the same as that in the hot water utilization mode of the first embodiment. However, there is a difference in that the compressor flow path 20a is bypassed before flowing from the first three-way valve 23 to the radiator 31, and the cooling water discharged from the second pump 22 passes through the heater 63. That is, the cooling water circulates in the order of the chiller 14, the first three-way valve 23, the radiator 31, the fourth three-way valve 26, the second pump 22, the heater 63, and the chiller 14. As a result, the cold heat is discarded to the external heat medium AA by the radiator 31. Since the heater 63 is off, the cooling water passing through the heater 63 is not heated by the heater 63. Thus, in the hot water utilization mode A of the present embodiment, the cooling water does not flow through the compressor flow path 20a.

[0217] In the hot water utilization mode B, as shown in FIG. 28, the second shut-off valve 30 opens, the third shut-off valve 62 closes, the port on the compressor flow path 20a side of the sixth three-way valve 28 opens and the port on the chiller 14 side closes, and the heater 63 is turned on. The opening / closing states of the other valves and the operating states of the compressor 11, the pumps 21 and 22 are the same as those in the hot water utilization mode A. At this time, the hot water circuit in which the cooling water is heated by the water-cooled condenser 12 has the same path as that in the hot water utilization mode A. As a result, hot water is supplied to the utilization side in the same manner as in the first embodiment.

[0218] Also at this time, the circulation path of the chilled water circuit in which the cooling water is cooled by the chiller 14 is the same as that in the hot water utilization mode A except for the path from the second pump 22 to the chiller 14 along the flow of the cooling water. The cooling water discharged from the second pump 22 is heated by the heater 63. As a result, the cooling water is maintained in a state that is hotter than the compression mechanism 11a of the compressor 11 in an extremely low temperature state. The cooling water heated by the heater 63 flows into the compressor flow path 20a from the sixth three-way valve 28 and heats the compression mechanism 11a in the compressor flow path 20a. The cooling water that has exited the compressor flow path 20a flows into the chiller 14 via the second shut-off valve 30 and is cooled.

[0219] When the compression mechanism 11a is in an extremely low temperature state, there is a risk that the compression mechanism 11a may not be able to perform sufficient work due to the decrease in the temperature and pressure of the refrigerant in the refrigeration cycle 10. Also, when the compression mechanism 11a is in an extremely low temperature state, there is also a risk that the frictional resistance of the lubricating oil in the compression mechanism 11a increases. That is, when the compression mechanism 11a is in an extremely low temperature state, the performance of the compression mechanism 11a may decrease. In contrast, as described above, by heating the compression mechanism 11a with the cooling water flowing through the compressor flow path 20a, a decrease in the performance of the compression mechanism 11a can be suppressed.

[0220] In the cold water utilization mode, as shown in FIG. 29, the additional three-way valve 61 has the port on the compressor flow path 20a side opened and the port on the water-cooled condenser 12 side blocked. Also, the third shut-off valve 62 is opened. Also, the sixth three-way valve 28 has the port on the chiller 14 side opened and the port on the compressor flow path 20a side closed. Also, the second shut-off valve 30 is closed. Also, the heater 63 is turned off. The opening and closing states of the other valves and the operating states of the compressor 11, pumps 21, 22 are the same as those in the cold water utilization mode of the first embodiment.

[0221] At this time, the cooling water that flows out from the second pump 22 and then flows into the chiller 14 after passing through the heater 63 and the sixth three-way valve 28 bypasses the compressor flow path 20a and flows into the chiller 14. The other paths of the cold water circuit in which the cooling water is cooled by the chiller 14 are the same as those in the cold water utilization mode of the first embodiment. Thereby, as in the first embodiment, cold water is supplied to the utilization side. Note that since the heater 63 is not operating, the cooling water passing through the heater 63 is not heated by the heater 63.

[0222] Regarding the hot water circuit in which the cooling water is heated by the water-cooled condenser 12, the cooling water flowing out of the first pump 21 flows through the compressor flow path 20a from the additional three-way valve 61, and then enters the water-cooled condenser 12 via the third shut-off valve. The other paths of the hot water circuit are the same as those in the cold water utilization mode of the first embodiment. That is, the cooling water circulates in the order of the water-cooled condenser 12, the third three-way valve 25, the radiator 31, the fourth three-way valve 26, the first pump 21, the additional three-way valve 61, the compressor flow path 20a, the third shut-off valve 62, and the water-cooled condenser 12.

[0223] Thereby, in the cold water utilization mode, the cooling water that has been cooled by heat dissipation in the radiator 31 and whose temperature has decreased is used to cool the compressor 11 (more specifically, the compression mechanism 11a, etc.) in the compressor flow path 20a before being reheated by the water-cooled condenser 12.

[0224] During the operation of the compressor 11, the temperature of the compressor 11 often becomes higher than the temperature of the cooling water heated by the chiller 14. In such a case, by cooling the compressor 11 with the hot water heated by the water-cooled condenser 12 instead of the cold water cooled by the chiller 14 and supplied to the utilization side, it is possible to cool the compressor 11 while suppressing the possibility of interfering with the cooling effect on the utilization side.

[0225] In this embodiment, the sixth three-way valve 28, the second shut-off valve 30, the additional three-way valve 61, and the third shut-off valve 62 constitute a multi-switching mechanism for switching the path for guiding the cooling water to the compressor flow path 20a in the cooling water flow path 20. And in the cold water circuit in the hot water utilization mode B, the path from the sixth three-way valve 28 to the inlet side end of the compressor flow path 20a and the path from the outlet side end of the compressor flow path 20a to the chiller 14 are cooling paths. And in the hot water circuit in the cold water utilization mode, the path from the additional three-way valve 61 to the inlet side end of the compressor flow path 20a and the path from the outlet side end of the compressor flow path 20a to the water-cooled condenser 12 are heating paths.

[0226] The modifications such as those of the present embodiment with respect to the first embodiment are also applicable to the third to thirteenth embodiments. Further, the same effects can be obtained from the configurations similar to those of the present embodiment in the first to thirteenth embodiments.

[0227] (Other embodiments) Note that the present invention is not limited to the above-described embodiments, and can be modified as appropriate. Further, the above-described multiple embodiments are not independent of each other, and can be combined as appropriate, except in cases where the combination is clearly impossible. Also, in the above embodiments, the elements constituting the embodiments are not necessarily essential, except in cases where it is clearly stated that they are essential and cases where they are considered to be clearly essential in principle. Also, in the above embodiments, when numerical values such as the number, numerical value, amount, and range of the components of the embodiment are mentioned, they are not limited to that specific number, except in cases where it is clearly stated that they are essential and cases where they are clearly limited to a specific number in principle. In particular, when a plurality of values are exemplified for a certain amount, values between those plurality of values can also be adopted, except in cases where it is specifically stated otherwise and cases where it is clearly impossible in principle. Also, in the above embodiments, when referring to the shape, positional relationship, etc. of the components, etc., they are not limited to that shape, positional relationship, etc., except in cases where it is clearly stated otherwise and cases where they are clearly limited to a specific shape, positional relationship, etc. in principle. Further, the present invention also allows the following modification examples and modification examples within the equivalent range with respect to the above embodiments. Note that each of the following modification examples can independently select whether to apply or not apply to the above embodiments. That is, any combination, excluding clearly contradictory combinations among the following modification examples, can be applied to the above embodiments. For example, there may be modification examples as described later.

[0228] (Modification Example 1) In the above-described third embodiment, the compressor flow path 20a is configured such that the cooling water exchanges heat with the compression mechanism 11a and the inverter circuit 11c. Further, in the above-described thirteenth embodiment, the compressor flow path 20a is configured such that the cooling water exchanges heat with the compression mechanism 11a and the motor 11b. However, the compressor flow path 20a may be configured such that the cooling water exchanges heat with the compression mechanism 11a, the motor 11b, and the inverter circuit 11c.

[0229] (Modification Example 2) In the above-described embodiment, even when the path before the cooling water flows into the compressor flow path 20a in the cooling water flow path 20 changes, the path of the cooling water in the compressor flow path 20a remains unchanged. However, it is not necessarily the case.

[0230] (Modification Example 3) The temperature control device 1 according to the above-described embodiment is mounted on a vehicle, but it may be mounted on other than a vehicle. For example, the temperature control device 1 may be disposed inside a building such as a building.

[0231] (Modification Example 4) The refrigeration cycle 10 in the above-described embodiment has the water-cooled condenser 12 and the chiller 14 as heat exchangers. However, the refrigeration cycle 10 may have other heat reciprocating machines. For example, the refrigeration cycle 10 may have an evaporator that cools the air-conditioning air CA by exchanging heat between the refrigerant decompressed and expanded by the expansion valve 13 and the air-conditioning air CA.

[0232] (Modification Example 5) In the temperature control device 1 of the first embodiment, the refrigeration cycle 10, the three-way valves 23 to 28, the pumps 21 and 22, the shut-off valves 29 and 30, and the cooling water flow path connecting them may be formed as one module. Alternatively, the pumps 21 and 22, the refrigeration cycle 10, the cooling water flow path connecting the pump 21 and the water-cooled condenser 12 of the refrigeration cycle 10, and the cooling water flow path connecting the pump 22 and the chiller 14 of the refrigeration cycle 10 may be formed as one module.

[0233] (Features of the Present Invention) Claim 1 A temperature control device for adjusting the temperature of temperature control targets (BT, CA), comprising a refrigeration cycle (10) in which a refrigerant circulates, a cooling water flow path (20) for supplying cooling water to a utilization side heat exchanger (32, 33, 34) for heat-exchanging the temperature control target with the cooling water and a radiator (31) for heat-exchanging the heat medium (AA) with the cooling water, wherein the refrigeration cycle has a compressor (11) that compresses and discharges a refrigerant, a condenser (12) that heats the cooling water by heat-exchanging the refrigerant compressed by the compressor with the cooling water flowing through the cooling water flow path, an expansion valve (13) that decompresses the refrigerant flowing out from the condenser, and a chiller (14) that cools the cooling water by heat-exchanging the refrigerant decompressed by the expansion valve with the cooling water flowing through the cooling water flow path, of the cooling water heated by the condenser and the cooling water cooled by the chiller, one of the cooling waters flows through the utilization side heat exchanger and exchanges heat with the temperature control target, and the other cooling water exchanges heat with the heat medium in the radiator, and the cooling water flow path has a compressor flow path (20a) for cooling or heating the compressor, the temperature control device. Claim 2 The compressor has a housing (125) and a movable member (141) surrounded by the housing, a compression chamber (423) is formed between the housing and the movable member, when the movable member moves, the refrigerant is introduced into the compression chamber, compressed in the compression chamber, and then discharged, The temperature control device according to claim 1, wherein the compressor flow path has a heat exchange passage (853) formed inside the housing. Claim 3 The compressor flow path is a flow path for cooling the compressor, when the movable member moves, the refrigerant is introduced into the compression chamber from the suction port (422), compressed in the compression chamber, and then discharged from the discharge port (421), In the housing, the surface area of the heat exchange passage per unit volume in a portion closer to the discharge port than the suction port is larger than the surface area of the heat exchange passage per unit volume in a portion closer to the suction port than the discharge port. The temperature control device according to claim 2. [Claim 4] The flow path for the compressor is configured such that the cooling water cooled by the chiller flows therethrough. The temperature control device according to any one of claims 1 to 3. [Claim 5] The temperature control device according to any one of claims 1 to 3, having a multi-switching mechanism (23, 28, 30, 36, 41, 61, 62) that switches the path for guiding the cooling water to the flow path for the compressor in the cooling water flow path. [Claim 6] The multi-switching mechanism switches between a first cooling path that guides the cooling water cooled by the chiller to the flow path for the compressor before the cooling water flows into the radiator, and a second cooling path that guides the cooling water cooled by the chiller to the flow path for the compressor after the cooling water flows into the utilization-side heat exchanger and before the cooling water returns to the chiller. The temperature control device according to claim 5. [Claim 7] The temperature control device according to any one of claims 1 to 6, having a cooling / non-cooling switching mechanism (36) that switches between a path in which the cooling water cooled by the chiller cools the compressor and flows into the radiator, and a path in which the cooling water cooled by the chiller bypasses the compressor and flows into the radiator. [Claim 8] The cooling water flow path is configured such that the cooling water heated by the condenser flows through the flow path for the compressor. The temperature control device according to any one of claims 1 to 3. [Claim 9] The cooling water flow path is configured such that the cooling water heated by the condenser cools the compressor by flowing through the flow path for the compressor. The temperature control device according to claim 8. [Claim 10] The temperature control device according to claim 8 or 9, wherein the cooling water flow path is configured to cool the compressor by allowing the cooling water heated by the condenser and then cooled by the radiator to flow through the compressor flow path. [Claim 11] The compressor includes a compression mechanism (11a) that sucks and compresses a refrigerant and discharges the compressed refrigerant that has become high-temperature and high-pressure, a motor (11b) that generates power for driving the compression mechanism, and an inverter circuit (11c) that supplies power for power generation to the motor. The temperature control device according to any one of claims 1 to 10, wherein the compressor flow path includes a flow path for heat-exchanging the inverter circuit and the cooling water. [Claim 12] The compressor includes a compression mechanism (11a) that sucks and compresses a refrigerant and discharges the compressed refrigerant that has become high-temperature and high-pressure, a motor (11b) that generates power for driving the compression mechanism, and an inverter circuit (11c) that supplies power for power generation to the motor. The temperature control device according to any one of claims 1 to 11, wherein the compressor flow path includes a flow path for heat-exchanging the motor and the cooling water. [Claim 13] The temperature control device according to any one of claims 1 to 12, wherein the compressor flow path has a plurality of sub-flow paths arranged in parallel and an adjustment unit (11d) that adjusts the flow rate of at least a part of the plurality of sub-flow paths.

Explanation of Signs

[0234] BT… Battery, CA… Air-conditioning air, 1… Temperature control device, 10… Refrigeration cycle, 11… Compressor, 11a… Compression mechanism, 11b… Motor, 11c… Inverter circuit, 11d… Adjustment unit, 12… Water-cooled condenser, 13… Expansion valve, 14… Chiller, 20… Cooling water flow path, Compressor flow path, 23… First three-way valve, 28… Sixth three-way valve, 30… Second shut-off valve, 32… Cooler core, 33… Heater core, 34… Battery heat exchanger, 36… Seventh three-way valve, 125… Third middle housing, 141… Piston rotor, 421… Discharge port, 422… Suction port, 423… Compression chamber, 853… Heat exchange passage.

Claims

1. A temperature control device for adjusting the temperature of temperature control targets (BT, CA), comprising: A refrigeration cycle (10) in which a refrigerant circulates; A cooling water flow path (20) for supplying cooling water to a utilization-side heat exchanger (32, 33, 34) for heat-exchanging the temperature control target with the cooling water, a radiator (31) for heat-exchanging the heat medium (AA) with the cooling water, and the cooling water; The refrigeration cycle includes a compressor (11) that compresses and discharges a refrigerant, a condenser (12) that heats the cooling water by heat-exchanging the refrigerant compressed by the compressor with the cooling water flowing through the cooling water flow path, an expansion valve (13) that decompresses the refrigerant flowing out from the condenser, and a chiller (14) that cools the cooling water by heat-exchanging the refrigerant decompressed by the expansion valve with the cooling water flowing through the cooling water flow path; Of the cooling water heated by the condenser and the cooling water cooled by the chiller, one of the cooling waters flows through the utilization-side heat exchanger and exchanges heat with the temperature control target, and the other cooling water exchanges heat with the heat medium in the radiator; The cooling water flow path has a compressor flow path (20a) for cooling or heating the compressor; The compressor flow path is a flow path for heating the compressor with cooling water, and is a temperature control device.

2. A temperature control device for adjusting the temperature of temperature control targets (BT, CA), comprising: A refrigeration cycle (10) in which a refrigerant circulates; A cooling water flow path (20) for supplying cooling water to a utilization-side heat exchanger (32, 33, 34) for heat-exchanging the temperature control target with the cooling water, a radiator (31) for heat-exchanging the heat medium (AA) with the cooling water, and the cooling water; The refrigeration cycle includes a compressor (11) that compresses and discharges a refrigerant, a condenser (12) that heats cooling water by exchanging heat between the refrigerant compressed by the compressor and the cooling water flowing through the cooling water flow path, an expansion valve (13) that decompresses the refrigerant flowing out from the condenser, and a chiller (14) that cools the cooling water by exchanging heat between the refrigerant decompressed by the expansion valve and the cooling water flowing through the cooling water flow path. Among the cooling water heated by the condenser and the cooling water cooled by the chiller, one of the cooling waters flows through the utilization-side heat exchanger and exchanges heat with the temperature control target, and the other cooling water exchanges heat with the heat medium in the radiator. The cooling water flow path has a compressor flow path (20a) for cooling or heating the compressor. In the hot water utilization mode, the cooling water heated by the condenser warms the temperature control target in the utilization-side heat exchanger, and the cooling water cooled by the chiller absorbs heat in the radiator. A temperature control device in which, in the hot water utilization mode, when there is no frosting on the radiator, the cooling water flows through the compressor flow path after being cooled by the chiller and before being heated by the radiator.

3. A temperature control device for adjusting the temperature of a temperature control target (BT, CA), comprising: A refrigeration cycle (10) in which a refrigerant circulates; A utilization-side heat exchanger (32, 33, 34) for exchanging heat between the temperature control target and cooling water, and a cooling water flow path (20) for supplying cooling water to a radiator (31) for exchanging heat between the heat medium (AA) and the cooling water. The refrigeration cycle includes a compressor (11) that compresses and discharges a refrigerant, a condenser (12) that heats cooling water by exchanging heat between the refrigerant compressed by the compressor and the cooling water flowing through the cooling water flow path, an expansion valve (13) that decompresses the refrigerant flowing out from the condenser, and a chiller (14) that cools the cooling water by exchanging heat between the refrigerant decompressed by the expansion valve and the cooling water flowing through the cooling water flow path. Of the cooling water heated by the capacitor and the cooling water cooled by the chiller, one of the cooling waters flows through the utilization-side heat exchanger and exchanges heat with the temperature control target, and the other cooling water exchanges heat with the heat medium in the radiator. The cooling water flow path has a compressor flow path (20a) for cooling or heating the compressor. The temperature control device has a multi-switching mechanism (23, 28, 30, 36, 41, 61, 62) that switches the path for guiding cooling water to the compressor flow path in the cooling water flow path.

4. A temperature control device for adjusting the temperature of a temperature control target (BT, CA), A refrigeration cycle (10) in which a refrigerant circulates, A utilization-side heat exchanger (32, 33, 34) for exchanging heat between the temperature control target and cooling water, and a cooling water flow path (20) for supplying cooling water to a radiator (31) for exchanging heat between the heat medium (AA) and the cooling water. The refrigeration cycle includes a compressor (11) that compresses and discharges a refrigerant, a capacitor (12) that heats the cooling water by exchanging heat between the refrigerant compressed by the compressor and the cooling water flowing through the cooling water flow path, an expansion valve (13) that decompresses the refrigerant flowing out of the capacitor, and a chiller (14) that cools the cooling water by exchanging heat between the refrigerant decompressed by the expansion valve and the cooling water flowing through the cooling water flow path. Of the cooling water heated by the capacitor and the cooling water cooled by the chiller, one of the cooling waters flows through the utilization-side heat exchanger and exchanges heat with the temperature control target, and the other cooling water exchanges heat with the heat medium in the radiator. The cooling water flow path has a compressor flow path (20a) for cooling or heating the compressor. The compressor has a housing (125) and a movable member (141) surrounded by the housing. A compression chamber (423) is formed between the housing and the movable member. When the movable member moves, the refrigerant is introduced from the suction port (422) into the compression chamber, compressed in the compression chamber, and then discharged from the discharge port (421). The compressor flow path has a heat exchange passage (853) formed inside the housing. The compressor flow path is a flow path for cooling the compressor. A temperature control device, wherein the surface area per unit volume of the heat exchange passage in a portion of the housing closer to the discharge port than the suction port is larger than the surface area per unit volume of the heat exchange passage in a portion of the housing closer to the suction port than the discharge port. **Claim 5** The compressor flow path is a flow path for cooling the compressor with cooling water. The temperature control device according to any one of claims 1 to 4, wherein the compressor is not provided with a heat storage portion for storing the heat of the compressor. **Claim 6** The temperature control device according to claim 3, wherein the compressor flow path is a flow path for heating the compressor with cooling water. **Claim 7** In the hot water utilization mode, the cooling water heated by the condenser warms the temperature control target in the utilization-side heat exchanger, and the cooling water cooled by the chiller absorbs heat in the radiator. The temperature control device according to claim 3 or 4, wherein in the hot water utilization mode, when there is no frosting on the radiator, the cooling water flows through the compressor flow path after being cooled by the chiller and before being heated by the radiator. **Claim 8** The temperature control device according to claim 3, wherein the multi-switching mechanism switches between a first cooling path that guides the cooling water cooled by the chiller to the compressor flow path before flowing into the radiator and a second cooling path that guides the cooling water cooled by the chiller to the compressor flow path after flowing into the utilization-side heat exchanger and before returning to the chiller. **Claim 9** The temperature control device according to claim 3 or 4, wherein the flow path for the compressor is configured such that the cooling water cooled by the chiller flows therethrough.

10. The temperature control device according to any one of claims 2 to 4, further comprising a cooling / non-cooling switching mechanism (36) that switches between a path in which the cooling water cooled by the chiller cools the compressor and flows into the radiator and a path in which the cooling water cooled by the chiller bypasses the compressor and flows into the radiator.

11. The temperature control device according to claim 3 or 4, wherein the cooling water flow path is configured such that the cooling water heated by the condenser flows through the flow path for the compressor.

12. The temperature control device according to claim 11, wherein the cooling water flow path is configured such that the cooling water heated by the condenser flows through the flow path for the compressor to cool the compressor.

13. The temperature control device according to claim 11, wherein the cooling water flow path is configured such that the cooling water heated by the condenser and then cooled by the radiator flows through the flow path for the compressor to cool the compressor.

14. The compressor includes a compression mechanism (11a) that sucks and compresses a refrigerant and discharges the compressed refrigerant at a high temperature and high pressure, a motor (11b) that generates power for driving the compression mechanism, and an inverter circuit (11c) that supplies power for power generation to the motor. The temperature control device according to any one of claims 1 to 4, wherein the flow path for the compressor includes a flow path for heat exchange between the inverter circuit and the cooling water.

15. The compressor includes a compression mechanism (11a) that sucks and compresses a refrigerant and discharges the compressed refrigerant at a high temperature and high pressure, a motor (11b) that generates power for driving the compression mechanism, and an inverter circuit (11c) that supplies power for power generation to the motor. The flow path for the compressor includes a flow path for heat-exchanging the motor and the cooling water, and the temperature control device according to any one of claims 1 to 4.

16. The flow path for the compressor has a plurality of sub-flow paths arranged in parallel and an adjustment unit (11d) for adjusting the flow rate of at least a part of the plurality of sub-flow paths, and the temperature control device according to any one of claims 1 to 4.

Images