Refrigeration Cycle Equipment

Abstract

A refrigeration cycle device comprising a first evaporator (15, 17a) and a second evaporator (17, 17b) connected in parallel to the refrigerant flow, and an accumulator (18), wherein the accumulator (18) is disposed in a first path and / or a second path, where the first path is defined as the path of energy flow in which the heat of a first object to be cooled moves to the suction refrigerant that is to be sucked into a compressor (11), and the second path is defined as the path of energy flow in which the heat of a second object to be cooled moves to the suction refrigerant. The refrigeration cycle device further comprises: a first switching unit (16a, 20a, 20b) that switches so that the heat of the first object to be cooled moves bypassing the accumulator (18); and a second three-way valve (16b, 20a, 20b) that switches so that the heat of the second object to be cooled moves bypassing the accumulator (18).

Description

CROSS-REFERENCE TO RELATED APPLICATIONS

[0001] This application is based on Japanese Patent Application No. 2022-5681 filed on January 18, 2022, the contents of which are incorporated herein by reference. [Technical field]

[0002] The present disclosure relates to a refrigeration cycle device including a plurality of evaporators and accumulators. [Background technology]

[0003] Conventionally, Patent Document 1 discloses a refrigeration cycle device applied to a vehicle air conditioner. The refrigeration cycle device of Patent Document 1 includes a plurality of evaporators, such as a front seat evaporator and a rear seat evaporator. Furthermore, the refrigeration cycle device of Patent Document 1 includes an accumulator, which is a low-pressure side gas-liquid separator that accumulates excess refrigerant in the cycle.

[0004] In the refrigerant circuit of the refrigeration cycle device of Patent Document 1, the refrigerant outlet of the front seat evaporator is connected to the inlet side of the accumulator, and the refrigerant outlet of the rear seat evaporator is connected to the outlet side of the accumulator. In other words, in the refrigeration cycle device of Patent Document 1, the refrigerant flowing out of the front seat evaporator flows into the accumulator, and the refrigerant flowing out of the rear seat evaporator bypasses the accumulator and is guided to the suction port side of the compressor. [Prior art documents] [Patent documents]

[0005] [Patent Document 1] JP 2006-145170 A Summary of the Invention

[0006] In recent years, refrigeration cycle devices have been developed that include multiple evaporators and accumulators and are used to cool multiple types of objects to be cooled at different temperatures. For example, refrigeration cycle devices that are used in vehicle air conditioners mounted on electric vehicles are being developed to cool not only the air blown into the vehicle cabin, but also the battery and other on-board devices.

[0007] In a refrigeration cycle device that has multiple evaporator sections for cooling multiple types of cooling objects, when the temperature conditions of each cooling object change, it may become necessary to switch between an evaporator that supplies refrigerant and an evaporator that does not supply refrigerant.

[0008] However, in the refrigeration cycle device of Patent Document 1, if the refrigerant is not circulated through the front seat evaporator, the accumulator cannot store the excess refrigerant in the cycle, which may result in the refrigeration cycle device being unable to operate stably and the rear seat evaporator being unable to exert its cooling capacity.

[0009] In addition, in a refrigeration cycle device having multiple evaporators for cooling multiple types of objects to be cooled, it becomes necessary to appropriately adjust the cooling capacity of each evaporator depending on the temperature conditions of each object to be cooled, etc.

[0010] However, in the refrigeration cycle device of Patent Document 1, the cooling capacity of the rear seat evaporator can be adjusted relatively easily by changing the degree of superheat of the refrigerant on the outlet side of the rear seat evaporator, but it is difficult to adjust the cooling capacity of the front seat evaporator. This is because an accumulator is connected to the refrigerant outlet of the front seat evaporator, and the refrigerant on the outlet side of the front seat evaporator approaches saturated gas phase refrigerant.

[0011] In view of the above, an object of the present disclosure is to provide a refrigeration cycle apparatus including a plurality of evaporators and accumulators, which is capable of causing the evaporators to exhibit appropriate cooling capacity.

[0012] A refrigeration cycle device according to a first aspect of the present disclosure includes a first evaporator section, a second evaporator section, an accumulator, and a compressor.

[0013] The first and second evaporators evaporate the refrigerant circulating in the refrigerant circuit. The first and second evaporators are connected in parallel with respect to the flow of the refrigerant. The accumulator separates the refrigerant flowing out of at least one of the first and second evaporators into gas and liquid and stores the excess refrigerant. The compressor draws in and compresses the refrigerant flowing out of the accumulator.

[0014] Furthermore, the energy flow path along which heat from the first object to be cooled moves to the intake refrigerant drawn into the compressor via at least one of the first evaporator and the second evaporator is defined as a first path, and the energy flow path along which heat from the second object to be cooled moves to the intake refrigerant via at least one of the first evaporator and the second evaporator is defined as a second path.

[0015] The accumulator is disposed in at least one of the first path and the second path.

[0016] When the accumulator is disposed on the first path, a first bypass path and a first switch unit are provided.

[0017] The first bypass path is a path for transferring heat of the first object to be cooled by bypassing the accumulator. The first switching unit is capable of switching between a first flow mode in which the heat of the first object to be cooled is transferred via the accumulator, and a first bypass flow mode in which the heat of the first object to be cooled is transferred via the first bypass path.

[0018] When the accumulator is disposed on the second path, a second bypass path and a second switching unit are provided.

[0019] The second bypass path is a path for transferring heat of the second object to be cooled by bypassing the accumulator. The second switching unit is capable of switching between a second flow mode in which the heat of the second object to be cooled is transferred via the accumulator and a second bypass flow mode in which the heat of the second object to be cooled is transferred via the second bypass path.

[0020] According to this, the accumulator is disposed in at least one of the first path and the second path. Therefore, the refrigerant that has absorbed at least one of the heat of the first object to be cooled and the heat of the second object to be cooled in at least one of the first evaporation section and the second evaporation section can be made to flow into the accumulator. Then, the accumulator can store surplus refrigerant in the cycle.

[0021] As a result, the refrigeration cycle device can be operated stably, and the first evaporator section and the second evaporator section can be made to reliably exert their cooling capabilities.

[0022] Furthermore, when the first switching unit is provided, the first flow mode and the first bypass flow mode can be switched. Similarly, when the second switching unit is provided, the second flow mode and the second bypass flow mode can be switched.

[0023] According to this, the refrigerant flowing out of the first evaporator can be sucked into the compressor while bypassing the accumulator. Also, the refrigerant flowing out of the second evaporator can be sucked into the compressor while bypassing the accumulator. As a result, it is possible to adjust the cooling capacity of each evaporator.

[0024] Furthermore, the flow rate of the refrigerant flowing through the accumulator can be reduced to reduce the pressure loss that occurs in the refrigerant when it flows through the accumulator, which increases the pressure of the suctioned refrigerant and increases the discharge flow rate of the compressor, thereby increasing the cooling capacity of the evaporator.

[0025] That is, according to the refrigeration cycle device of the first aspect, it is possible to make the evaporator exhibit an appropriate cooling capacity.

[0026] Here, the energy flow can be defined as the flow of energy when energy is transmitted.

[0027] A refrigeration cycle device according to a second aspect of the present disclosure includes a first evaporator section, a second evaporator section, an accumulator, and a compressor.

[0028] The first and second evaporators evaporate the refrigerant circulating in the refrigerant circuit. The first and second evaporators are connected in parallel with respect to the flow of the refrigerant. The accumulator separates the refrigerant flowing out of at least one of the first and second evaporators into gas and liquid and stores the excess refrigerant. The compressor draws in and compresses the refrigerant flowing out of the accumulator.

[0029] The refrigerant coolant circulation system further includes a bypass passage and a refrigerant circuit switching unit.

[0030] The bypass passage guides at least one of the refrigerant flowing out of the first evaporator and the refrigerant flowing out of the second evaporator to the suction side of the compressor, bypassing the accumulator. The refrigerant circuit switching unit switches to a refrigerant circuit that causes at least one of the refrigerant flowing out of the first evaporator and the refrigerant flowing out of the second evaporator to flow into the accumulator.

[0031] According to this, the refrigerant circuit switching unit switches to a refrigerant circuit that causes at least one of the refrigerant flowing out of the first evaporation unit and the refrigerant flowing out of the second evaporation unit to flow into the accumulator, so that surplus refrigerant in the cycle can be stored in the accumulator.

[0032] As a result, the refrigeration cycle device can be stably operated, and the first evaporation section and the second evaporation section can be made to reliably exert their cooling capacity. That is, according to the refrigeration cycle device of the second aspect of the present disclosure, the evaporation sections can be made to exert appropriate cooling capacity.

[0033] A refrigeration cycle device according to a third aspect of the present disclosure includes a first evaporator section, a second evaporator section, an accumulator, a compressor, and a bypass passage.

[0034] The first and second evaporators evaporate the refrigerant circulating in the refrigerant circuit. The first and second evaporators are connected in parallel with respect to the flow of the refrigerant. The accumulator separates the refrigerant flowing out of the first evaporator into gas and liquid and stores the excess refrigerant. The compressor draws in and compresses the gas-phase refrigerant separated by the accumulator. The bypass passage guides the refrigerant flowing out of the second evaporator to the suction port side of the compressor, bypassing the accumulator.

[0035] The heat medium circuit and the heat medium circuit switching unit are further provided.

[0036] The heat medium circuit circulates a heat medium that transports heat from the first object to be cooled and the second object to be cooled. The heat medium circuit switching unit switches the heat medium that has absorbed at least one of the heat from the first object to be cooled and the heat from the second object to the heat medium circuit that exchanges heat with the refrigerant flowing through the first evaporator.

[0037] According to this, the heat medium circuit switching unit switches to a heat medium circuit that exchanges heat with the heat medium that has absorbed at least one of the heat of the first object to be cooled and the heat of the second object to be cooled, with the refrigerant flowing through the first evaporation unit. Therefore, the refrigerant that has exchanged heat with the heat medium in the first evaporation unit can be made to flow into the accumulator. Then, the accumulator can store surplus refrigerant in the cycle.

[0038] As a result, the refrigeration cycle apparatus can be stably operated, and the first evaporation section can be made to reliably exert a cooling capacity. That is, according to the refrigeration cycle apparatus of the third aspect of the present disclosure, the evaporation section can be made to exert an appropriate cooling capacity. [Brief description of the drawings]

[0039] The above and other objects, features and advantages of the present disclosure will become more apparent from the following detailed description taken in conjunction with the accompanying drawings. [Figure 1] 1 is a schematic overall configuration diagram of a refrigeration cycle device according to a first embodiment. [Diagram 2] 1 is a schematic overall configuration diagram showing a refrigerant flow and the like in a first cooling mode of a refrigeration cycle device of a first embodiment. FIG. [Diagram 3] FIG. 2 is a schematic overall configuration diagram showing a refrigerant flow and the like in a second cooling mode of the refrigeration cycle device of the first embodiment. [Figure 4] FIG. 2 is a schematic overall configuration diagram showing a refrigerant flow and the like in a first composite cooling mode of the refrigeration cycle device of the first embodiment. [Diagram 5] FIG. 2 is a schematic overall configuration diagram showing a refrigerant flow and the like in a second composite cooling mode of the refrigeration cycle device of the first embodiment. [Figure 6] FIG. 2 is a schematic overall configuration diagram showing a refrigerant flow and the like in a third composite cooling mode of the refrigeration cycle device of the first embodiment. [Figure 7] FIG. 5 is a schematic overall configuration diagram of a refrigeration cycle device according to a second embodiment. [Figure 8] FIG. 11 is a schematic overall configuration diagram showing a refrigerant flow and the like in a first cooling mode of a refrigeration cycle device of a second embodiment. [Figure 9] FIG. 11 is a schematic overall configuration diagram showing a refrigerant flow and the like in a second cooling mode of a refrigeration cycle device of a second embodiment. [Figure 10] FIG. 11 is a schematic overall configuration diagram showing a refrigerant flow and the like in a first composite cooling mode of a refrigeration cycle device of a second embodiment. [Figure 11] FIG. 11 is a schematic overall configuration diagram showing a refrigerant flow and the like in a second composite cooling mode of a refrigeration cycle device of a second embodiment. [Figure 12] FIG. 11 is a schematic overall configuration diagram of a refrigeration cycle device according to a third embodiment. [Figure 13] FIG. 13 is a schematic overall configuration diagram of a refrigeration cycle device according to a fourth embodiment. [Figure 14]FIG. 13 is a schematic overall configuration diagram of a refrigeration cycle device according to a fifth embodiment. [Figure 15] FIG. 13 is a schematic overall configuration diagram of a refrigeration cycle device according to a sixth embodiment. [Figure 16] FIG. 13 is a Mollier diagram showing a change in state of a refrigerant in a comparative operation mode of the refrigeration cycle device of the sixth embodiment. [Figure 17] FIG. 13 is a Mollier diagram showing a change in state of a refrigerant in a first composite cooling mode of the refrigeration cycle device of the sixth embodiment. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0040] Hereinafter, a number of embodiments for carrying out the present disclosure will be described with reference to the drawings. In each embodiment, the same reference numerals may be used to designate parts corresponding to matters described in the preceding embodiment, and duplicated descriptions may be omitted. In each embodiment, when only a part of the configuration is described, other embodiments described previously may be applied to other parts of the configuration. In addition to combinations of parts that are specifically indicated as being possible in each embodiment, it is also possible to partially combine embodiments even if not specified, as long as there is no particular problem with the combination.

[0041] (First embodiment) A first embodiment of a refrigeration cycle apparatus according to the present disclosure will be described with reference to Figs. 1 to 6. The refrigeration cycle apparatus 1 of this embodiment is applied to an air conditioner with an equipment cooling function that combines a function of air conditioning a space to be air-conditioned and a function of cooling a target equipment 70 to be cooled. Therefore, a first object to be cooled in the refrigeration cycle apparatus 1 is the blown air to be blown into the space to be air-conditioned. Also, a second object to be cooled in the refrigeration cycle apparatus 1 is the target equipment 70 to be cooled.

[0042] As shown in the overall configuration diagram of FIG. 1, the refrigeration cycle device 1 includes a vapor compression type refrigerant circuit 10, a heat medium circuit 30, a control device 50, and the like.

[0043] First, a description will be given of the refrigerant circuit 10. The refrigerant circuit 10 forms a vapor compression refrigeration cycle that cools the air to be blown to the space to be air-conditioned and the heat medium circulating in the heat medium circuit 30.

[0044] The refrigerant circuit 10 employs an HFO refrigerant (specifically, R1234yf) as the refrigerant. The refrigerant circuit 10 constitutes a subcritical refrigeration cycle in which the pressure of the high-pressure side refrigerant does not exceed the critical pressure of the refrigerant. The refrigerant is mixed with refrigerant oil for lubricating the compressor 11. The refrigerant oil is a PAG oil that is compatible with liquid-phase refrigerant. A portion of the refrigerant oil circulates through the refrigerant circuit 10 together with the refrigerant.

[0045] The compressor 11 draws in, compresses, and discharges refrigerant in the refrigerant circuit 10. The compressor 11 is an electric compressor whose refrigerant discharge capacity (i.e., rotation speed) is controlled by a control signal output from a control device 50 described later.

[0046] The discharge port of the compressor 11 is connected to the refrigerant inlet side of the radiator 12. The radiator 12 is disposed outside the space to be air-conditioned. The radiator 12 is a heat exchanger for heat dissipation that exchanges heat between the refrigerant discharged from the compressor 11 and the outside air blown by the outside air fan 12a. The radiator 12 dissipates heat contained in the discharged refrigerant to the outside air, condensing the discharged refrigerant. Therefore, the radiator 12 is a heat exchanger for condensation.

[0047] The outside air fan 12a is an electric blower whose blowing capacity (that is, rotation speed) is controlled by a control voltage output from the control device 50.

[0048] The inlet side of a first three-way joint 13a is connected to the outlet side of the heat radiator 12. The first three-way joint 13a has three inlet and outlet ports that communicate with each other. As the first three-way joint 13a, a joint portion formed by joining multiple pipes or a joint portion formed by providing multiple refrigerant passages in a metal block or a resin block can be used.

[0049] Furthermore, as described below, the refrigerant circuit 10 includes a second three-way joint 13b to a fourth three-way joint 13d. The second three-way joint 13b to the fourth three-way joint 13d have the same basic configuration as the first three-way joint 13a.

[0050] These three-way joints split the refrigerant flow when one of the three inlet / outlet ports is used as an inlet and the other two are used as outlet ports, and merge the refrigerant flow when two of the three inlet / outlet ports are used as inlet ports and the other is used as an outlet port.

[0051] An inlet side of a first expansion valve 14a is connected to one outlet of the first three-way joint 13a. A refrigerant inlet side of a cooling evaporator 15 is connected to an outlet of the first expansion valve 14a.

[0052] The first expansion valve 14a is a pressure reducing section on the cooling evaporator side that reduces the pressure of the refrigerant flowing out from one outlet of the first three-way joint 13a when cooling the air to be blown into the space to be air-conditioned. The first expansion valve 14a is a first flow rate adjusting section that adjusts the flow rate (in this embodiment, the mass flow rate) of the refrigerant flowing through the cooling evaporator 15.

[0053] The first expansion valve 14a is an electric variable throttle mechanism having a valve body that changes the throttle opening and an electric actuator as a drive unit that displaces the valve body. The operation of the first expansion valve 14a is controlled by a control signal output from the control device 50. The first expansion valve 14a has a full-closing function that closes the refrigerant passage by setting the throttle opening to a full-closing state.

[0054] The cooling evaporator 15 is a first evaporation section that exchanges heat between the low-pressure refrigerant decompressed by the first expansion valve 14a and the air blown from the indoor blower 15a. The cooling evaporator 15 evaporates the low-pressure refrigerant to exert a heat absorption effect, thereby cooling the air to be blown. The indoor blower 15a is an electric blower whose blowing capacity (i.e., rotation speed) is controlled by a control voltage output from the control device 50.

[0055] The inlet side of the first three-way valve 16a is connected to the refrigerant outlet of the cooling evaporator 15. The first three-way valve 16a is a three-way flow control valve that can continuously adjust the flow rate ratio between the flow rate of the refrigerant flowing out to one inlet side of the second three-way joint 13b and the flow rate of the refrigerant flowing out to one inlet side of the fourth three-way joint 13d. The operation of the first three-way valve 16a is controlled by a control signal output from the control device 50.

[0056] The other outlet of the first three-way joint 13a is connected to the inlet side of a second expansion valve 14b. The outlet of the second expansion valve 14b is connected to the refrigerant inlet side of a chiller 17.

[0057] The second expansion valve 14b is a pressure reducing section on the chiller side that reduces the pressure of the refrigerant flowing out from the other outlet of the first three-way joint 13a when cooling the heat medium circulating in the heat medium circuit 30. The second expansion valve 14b is a second flow rate adjusting section that adjusts the flow rate (in this embodiment, the mass flow rate) of the refrigerant flowing through the chiller 17. The basic configuration of the second expansion valve 14b is the same as that of the first expansion valve 14a. Therefore, the second expansion valve 14b also has a fully closing function.

[0058] The chiller 17 is a second evaporation section that exchanges heat between the low-pressure refrigerant decompressed by the second expansion valve 14b and the heat medium pumped from the heat medium pump 31. The chiller 17 evaporates the low-pressure refrigerant to exert a heat absorption effect, thereby cooling the heat medium.

[0059] The inlet side of the second three-way valve 16b is connected to the refrigerant outlet of the chiller 17. The second three-way valve 16b is a three-way flow control valve that can continuously adjust the flow rate ratio between the flow rate of the refrigerant flowing out to the other inlet side of the second three-way joint 13b and the flow rate of the refrigerant flowing out to one inlet side of the third three-way joint 13c. The basic configuration of the second three-way valve 16b is the same as that of the first three-way valve 16a.

[0060] The outlet of the second three-way joint 13b is connected to the inlet side of the accumulator 18. The accumulator 18 is a low-pressure side gas-liquid separator that separates the refrigerant that has flowed into it into gas and liquid and stores the separated refrigerant as surplus refrigerant in the cycle.

[0061] The other inlet side of the third three-way joint 13c is connected to the gas-phase refrigerant outlet of the accumulator 18. The other inlet side of the fourth three-way joint 13d is connected to the outlet side of the third three-way joint 13c. The suction side of the compressor 11 is connected to the outlet side of the fourth three-way joint 13d.

[0062] As is clear from the above description, the cooling evaporator 15 and the chiller 17 are connected in parallel with respect to the flow of the refrigerant. Furthermore, the first three-way valve 16a allows the refrigerant to flow out to the second three-way joint 13b, so that the refrigerant flowing out from the cooling evaporator 15 can flow into the accumulator 18. Furthermore, the first three-way valve 16a allows the refrigerant to flow out to the fourth three-way joint 13d, so that the refrigerant flowing out from the cooling evaporator 15 can be guided to the suction port side of the compressor 11, bypassing the accumulator 18.

[0063] Therefore, the first three-way valve 16a is a refrigerant circuit switching unit. The refrigerant passage connecting the first three-way valve 16a and the fourth three-way joint 13d forms a bypass passage. The refrigerant passage leading from the first three-way valve 16a to the suction port side of the compressor 11, bypassing the accumulator 18, is the first bypass passage 19a.

[0064] Furthermore, the second three-way valve 16b allows the refrigerant to flow out toward the second three-way joint 13b, so that the refrigerant that flows out from the chiller 17 can flow into the accumulator 18. The second three-way valve 16b allows the refrigerant to flow out toward the third three-way joint 13c, so that the refrigerant that flows out from the chiller 17 can be guided to the suction port side of the compressor 11, bypassing the accumulator 18.

[0065] Therefore, the second three-way valve 16b is a refrigerant circuit switching unit. The refrigerant passage connecting the second three-way valve 16b and the third three-way joint 13c forms a bypass passage. The refrigerant passage leading from the second three-way valve 16b to the suction port side of the compressor 11, bypassing the accumulator 18, is the second bypass passage 19b.

[0066] Next, the heat medium circuit 30 will be described. The heat medium circuit 30 is a circuit that circulates a heat medium. In this embodiment, an ethylene glycol aqueous solution is used as the heat medium. The heat medium circuit 30 is connected to a heat medium pump 31, a cooling water passage 70a formed in the device 70 to be cooled, a heat medium passage of the chiller 17, and the like.

[0067] The heat medium pump 31 is a heat medium pumping section that pumps the heat medium flowing out from the cooling water passage 70a of the cooled device 70 to the inlet side of the heat medium passage of the chiller 17. The heat medium pump 31 is an electric water pump whose rotation speed (i.e., pumping capacity) is controlled by a control voltage output from the control device 50.

[0068] An outlet side of the heat medium passage of the chiller 17 is connected to an inlet side of a cooling water passage 70a of the target device 70 to be cooled. The cooling water passage 70a is a cooling water passage formed to cool the target device 70 by circulating the heat medium cooled by the chiller 17.

[0069] Next, an overview of the electrical control unit of the refrigeration cycle apparatus 1 will be described. The control device 50 has a microcomputer including a CPU, ROM, RAM, etc., and its peripheral circuits. The control device 50 performs various calculations and processing based on a control program stored in the ROM. Then, the control device 50 controls the operation of various control target devices 11, 14a, 14b, 16a, 16b, 31, etc. connected to the output side based on the calculation and processing results.

[0070] A group of control sensors 51 for controlling various controlled devices is connected to the input side of the control device 50. Various detection signals detected by the group of sensors 51 are input to the control device 50. The group of control sensors 51 includes a high pressure temperature and pressure sensor, a first evaporator temperature and pressure sensor, a second evaporator temperature and pressure sensor, an inside air temperature sensor, an equipment temperature sensor, a heat medium temperature sensor, etc.

[0071] The high-pressure temperature and pressure sensor is a high-pressure temperature and pressure detection unit that detects the discharge refrigerant temperature Td, which is the temperature and pressure of the refrigerant discharged from the compressor 11. The first evaporator temperature and pressure sensor is a first evaporator temperature and pressure detection unit that detects the temperature and pressure of the refrigerant on the outlet side of the cooling evaporator 15. The second evaporator temperature and pressure sensor is a second evaporator temperature and pressure detection unit that detects the temperature and pressure of the refrigerant on the outlet side of the chiller 17.

[0072] The inside air temperature sensor is an inside air temperature detector that detects the temperature of the space to be air-conditioned. The equipment temperature sensor is an equipment temperature detector that detects the temperature of the equipment 70 to be cooled. The heat medium temperature sensor is a heat medium temperature detector that detects the heat medium temperature TW, which is the temperature of the heat medium flowing into the chiller 17.

[0073] Furthermore, an operation unit is connected to the input side of the control device 50 via a wired or wireless connection. An operation signal output from the operation unit is input to the control device 50. The operation unit is provided with various operation switches operated by a user. The various operation switches include an operation switch for requesting operation of the refrigeration cycle device 1, a mode changeover switch for setting an operation mode, and the like.

[0074] The control device 50 is an integrated configuration of a plurality of control units that control various control target devices connected to the output side of the control device 50. In other words, the components (hardware and software) of the control device 50 that control the operation of each control target device constitute the control units that control the operation of each control target device.

[0075] For example, in the control device 50, a component that controls the refrigerant discharge capacity of the compressor 11 is a discharge capacity control unit 50a. A component that controls the operation of the first three-way valve 16a and the second three-way valve 16b, which are refrigerant circuit switching units, is a refrigerant circuit control unit 50b. Note that, in FIG. 1, for clarity of illustration, some of the power lines or signal lines connecting the control device 50 and the controlled devices are omitted.

[0076] Next, the operation of the refrigeration cycle apparatus 1 of this embodiment in the above configuration will be described. In the refrigeration cycle apparatus 1, various operation modes are switched in order to cool the blown air and the equipment 70 to be cooled. The operation modes are switched by executing a control program stored in advance in the control device 50. When a user sets an operation mode using a mode change switch on the operation unit, the operation mode set by the user is given priority. The detailed operation of each operation mode will be described below.

[0077] (a) First cooling mode The first cooling mode is an operation mode in which only the blown air, which is the first cooling object, is cooled. In the first cooling mode, the control device 50 sets the first expansion valve 14a to a throttling state that exerts a decompression effect, and sets the second expansion valve 14b to a fully closed state.

[0078] In addition, the control device 50 controls the operation of the first three-way valve 16a so that the entire flow rate of the refrigerant flowing out from the cooling evaporator 15 flows into the accumulator .

[0079] In addition, the control device 50 controls the operation of the second three-way valve 16b so that the amount of refrigerant flowing out from the chiller 17 is guided to the suction port side of the compressor 11, bypassing the accumulator 18. Here, in the first cooling mode, the second expansion valve 14b is in a fully closed state, so that the refrigerant does not flow out from the chiller 17.

[0080] Therefore, in the refrigerant circuit 10 in the first cooling mode, as shown by the solid arrow in Figure 2, the refrigerant discharged from the compressor 11 is switched to a refrigerant circuit in which it circulates through the radiator 12, the first expansion valve 14a, the cooling evaporator 15, the first three-way valve 16a, the accumulator 18, and the suction port of the compressor 11 in that order.

[0081] The control device 50 also operates the indoor blower 15a. The control device 50 also appropriately controls the operation of various controlled devices so that the temperature of the blown air becomes an appropriate temperature for cooling the space to be air-conditioned.

[0082] Therefore, in the refrigerant circuit 10 in the first cooling mode, the radiator 12 functions as a condenser that radiates heat to condense the refrigerant, and the cooling evaporator 15 functions as an evaporator that evaporates the refrigerant, forming a vapor compression refrigeration cycle. The cooling evaporator 15 cools the blown air.

[0083] As a result, in the refrigeration cycle device 1 in the first cooling mode, the blown air cooled by the cooling evaporator 15 is blown out into the space to be air-conditioned, thereby realizing cooling of the space to be air-conditioned.

[0084] Here, the first path is indicated by a thick solid line in Fig. 2. The first path is a path of energy flow through which heat of the blown air, which is the first object to be cooled, moves to the intake refrigerant that is drawn into the compressor 11. The energy flow can be defined as the flow of energy when energy is transmitted.

[0085] In the refrigeration cycle apparatus 1, the accumulator 18 is disposed on the first path. The first bypass passage 19a serves as the first bypass path. The first three-way valve 16a serves as a first switching unit capable of adjusting the heat amount ratio of the heat amount (i.e., the amount of energy) of the heat possessed by the first object to be cooled to the accumulator 18 to the heat amount to be flowed into the first bypass passage 19a. In the first cooling mode, the first three-way valve 16a is switched to the first circulation mode.

[0086] (b) Second cooling mode The second cooling mode is an operation mode in which only the cooling target device 70, which is the second cooling target, is cooled. In the second cooling mode, the control device 50 puts the first expansion valve 14a in a fully closed state and the second expansion valve 14b in a throttling state.

[0087] In addition, the control device 50 controls the operation of the second three-way valve 16b so that the entire flow rate of the refrigerant flowing out from the chiller 17 flows into the accumulator 18.

[0088] In addition, the control device 50 controls the operation of the first three-way valve 16a so that the refrigerant flowing out from the cooling evaporator 15 is guided to the suction port side of the compressor 11, bypassing the accumulator 18. Here, in the second cooling mode, the first expansion valve 14a is in a fully closed state, so that the refrigerant does not flow out from the cooling evaporator 15.

[0089] Therefore, in the refrigerant circuit 10 in the second cooling mode, as shown by the solid arrows in Figure 3, the refrigerant discharged from the compressor 11 is switched to a refrigerant circuit in which it circulates through the radiator 12, the second expansion valve 14b, the chiller 17, the second three-way valve 16b, the accumulator 18, and the suction port of the compressor 11 in that order.

[0090] The control device 50 also operates the heat medium pump 31. The control device 50 also appropriately controls the operation of various controlled devices so that the temperature of the cooling target device 70 is kept at an appropriate temperature.

[0091] Therefore, in the refrigerant circuit 10 in the second cooling mode, a vapor compression refrigeration cycle is configured in which the radiator 12 functions as a condenser and the chiller 17 functions as an evaporator. The heat medium is cooled in the chiller 17. In the heat medium circuit 30 in the second cooling mode, the heat medium flowing out of the heat medium passage of the chiller 17 is pumped to the cooling water passage 70a of the device 70 to be cooled, as shown by the dashed arrow in FIG.

[0092] As a result, in the refrigeration cycle apparatus 1 in the second cooling mode, the heat medium cooled by the chiller 17 flows through the cooling water passage 70a of the equipment 70 to be cooled, thereby cooling the equipment 70 to be cooled.

[0093] Here, the second path is indicated by a thick dashed line in Fig. 3. The second path is a path of energy flow through which heat possessed by the cooling target device 70, which is the second object to be cooled, moves to the intake refrigerant.

[0094] In the refrigeration cycle apparatus 1, the accumulator 18 is disposed on the second path. The second bypass passage 19b serves as the second bypass path. The second three-way valve 16b serves as a second switching unit capable of adjusting the heat amount ratio of the heat amount of the second object to be cooled that is to be caused to flow into the second bypass passage 19b relative to the heat amount that is to be caused to flow into the accumulator 18. In the second cooling mode, the second three-way valve 16b is switched to the second circulation mode.

[0095] (c) Combined cooling mode The composite cooling mode is an operation mode for cooling both the blown air and the cooled device 70. The composite cooling modes include (c-1) a first composite cooling mode, (c-2) a second composite cooling mode, and (c-3) a third composite cooling mode.

[0096] (c-1) First combined cooling mode The first composite cooling mode is selected when the circuit configuration of the refrigerant circuit 10 is switched so that the enthalpy of the refrigerant on the outlet side of the chiller 17 is higher than that of the refrigerant on the outlet side of the cooling evaporator 15, and the refrigerant on the outlet side of the chiller 17 becomes a gas-phase refrigerant having a degree of superheat.

[0097] In the refrigerant circuit 10 in the first composite cooling mode, the controller 50 puts the first expansion valve 14a in a throttling state, and puts the second expansion valve 14b in a throttling state.

[0098] The control device 50 also controls the operation of the first three-way valve 16a so that the refrigerant flowing out from the cooling evaporator 15 flows into the accumulator 18. The control device 50 also controls the operation of the second three-way valve 16b so that the refrigerant flowing out from the chiller 17 is guided to the suction port side of the compressor 11, bypassing the accumulator 18.

[0099] 4, in the refrigerant circuit 10 in the first combined cooling mode, the refrigerant discharged from the compressor 11 circulates in the order of the radiator 12, the first expansion valve 14a, the cooling evaporator 15, the first three-way valve 16a, the accumulator 18, and the suction port of the compressor 11. At the same time, the refrigerant circuit is switched to one in which the refrigerant discharged from the compressor 11 circulates in the order of the radiator 12, the second expansion valve 14b, the chiller 17, the second three-way valve 16b, and the suction port of the compressor 11.

[0100] The control device 50 also operates the indoor blower 15a. The control device 50 also operates the heat medium pump 31. The control device 50 also appropriately controls the operation of various controlled devices so that the temperature of the blown air becomes appropriate for cooling the air-conditioned space, and the temperature of the cooling target device 70 becomes appropriate.

[0101] Therefore, in the refrigerant circuit 10 in the first composite cooling mode, a vapor compression refrigeration cycle is configured in which the radiator 12 functions as a condenser, and the cooling evaporator 15 and the chiller 17 function as evaporators. The cooling evaporator 15 cools the blown air. The chiller 17 cools the heat medium.

[0102] In the heat medium circuit 30 in the first composite cooling mode, the heat medium flowing out of the heat medium passage of the chiller 17 is pumped to the coolant passage 70a of the device 70 to be cooled, as indicated by the dashed arrow in FIG.

[0103] As a result, in the refrigeration cycle apparatus 1 in the first composite cooling mode, the blown air cooled by the cooling evaporator 15 is blown into the space to be air-conditioned, thereby cooling the space to be air-conditioned. Also, the heat medium cooled by the chiller 17 flows through the cooling water passage 70a of the equipment to be cooled 70, thereby cooling the equipment to be cooled 70.

[0104] In Fig. 4, the first path is indicated by a thick solid line, and the second path is indicated by a thick dashed line. In the first composite cooling mode, the first three-way valve 16a is switched to the first flow mode. Furthermore, in the first composite cooling mode, the second three-way valve 16b is switched to the second bypass flow mode.

[0105] In the first combined cooling mode, the refrigerant flowing out from the air-conditioning evaporator 15 is caused to flow into the accumulator 18, and the gas-phase refrigerant having a degree of superheat flowing out from the chiller 17 is guided to the suction port side of the compressor 11, bypassing the accumulator 18. As a result, in the first combined cooling mode, the enthalpy difference obtained by subtracting the enthalpy of the refrigerant on the inlet side from the enthalpy of the refrigerant on the outlet side of the chiller 17 is increased, and the cooling capacity of the chiller 17 can be increased.

[0106] (c-2) Second composite cooling mode The second composite cooling mode is selected when the circuit configuration of the refrigerant circuit 10 is switched so that the enthalpy of the refrigerant on the outlet side of the cooling evaporator 15 is higher than the enthalpy of the refrigerant on the outlet side of the chiller 17 and the refrigerant on the outlet side of the cooling evaporator 15 becomes a gas-phase refrigerant having a degree of superheat.

[0107] In the refrigerant circuit 10 in the second composite cooling mode, the controller 50 puts the first expansion valve 14a in a throttling state, and the second expansion valve 14b in a throttling state.

[0108] The control device 50 also controls the operation of the first three-way valve 16a so that the refrigerant flowing out from the cooling evaporator 15 is guided to the suction port side of the compressor 11, bypassing the accumulator 18. The control device 50 also controls the operation of the second three-way valve 16b so that the refrigerant flowing out from the chiller 17 flows into the accumulator 18.

[0109] 5, in the refrigerant circuit 10 in the second combined cooling mode, the refrigerant discharged from the compressor 11 circulates in the order of the radiator 12, the first expansion valve 14a, the cooling evaporator 15, the first three-way valve 16a, and the suction port of the compressor 11. At the same time, the refrigerant circuit is switched to one in which the refrigerant discharged from the compressor 11 circulates in the order of the radiator 12, the second expansion valve 14b, the chiller 17, the second three-way valve 16b, the accumulator 18, and the suction port of the compressor 11.

[0110] The control device 50 also operates the indoor blower 15a. The control device 50 also operates the heat medium pump 31. The control device 50 also appropriately controls the operation of various controlled devices so that the temperature of the blown air becomes appropriate for cooling the air-conditioned space, and the temperature of the cooling target device 70 becomes appropriate.

[0111] Therefore, in the refrigerant circuit 10 in the second composite cooling mode, a vapor compression refrigeration cycle is configured in which the radiator 12 functions as a condenser, and the cooling evaporator 15 and the chiller 17 function as evaporators. The cooling evaporator 15 cools the blown air. The chiller 17 cools the heat medium.

[0112] In the heat medium circuit 30 in the second composite cooling mode, the heat medium flowing out of the heat medium passage of the chiller 17 is pumped to the coolant passage 70a of the device 70 to be cooled, as indicated by the dashed arrow in FIG.

[0113] As a result, in the refrigeration cycle apparatus 1 in the second composite cooling mode, the blown air cooled by the cooling evaporator 15 is blown into the space to be air-conditioned, thereby cooling the space to be air-conditioned. Also, the heat medium cooled by the chiller 17 flows through the cooling water passage 70a of the equipment to be cooled 70, thereby cooling the equipment to be cooled 70.

[0114] In Fig. 5, the first path is indicated by a thick solid line, and the second path is indicated by a thick dashed line. In the second composite cooling mode, the first three-way valve 16a is switched to the first bypass flow mode. Furthermore, in the second composite cooling mode, the second three-way valve 16b is switched to the second flow mode.

[0115] In the second combined cooling mode, the refrigerant flowing out from the chiller 17 is caused to flow into the accumulator 18, and the gas-phase refrigerant having a degree of superheat flowing out from the cooling evaporator 15 is led to the suction port side of the compressor 11, bypassing the accumulator 18. As a result, in the second combined cooling mode, the enthalpy difference obtained by subtracting the enthalpy of the refrigerant on the inlet side from the enthalpy of the refrigerant on the outlet side of the cooling evaporator 15 is increased, and the cooling capacity of the cooling evaporator 15 can be increased.

[0116] (c-3) Third composite cooling mode The third composite cooling mode is a composite cooling mode selected when the first composite cooling mode and the second composite cooling mode are not selected. In the refrigerant circuit 10 in the third composite cooling mode, the control device 50 sets the first expansion valve 14a to a throttling state and the second expansion valve 14b to a throttling state.

[0117] The control device 50 also controls the operation of the first three-way valve 16a so that the refrigerant flowing out from the cooling evaporator 15 flows into the accumulator 18. The control device 50 also controls the operation of the second three-way valve 16b so that the refrigerant flowing out from the chiller 17 flows into the accumulator 18.

[0118] 6, the refrigerant discharged from the compressor 11 circulates through the radiator 12, the first expansion valve 14a, the cooling evaporator 15, the first three-way valve 16a, the accumulator 18, and the suction port of the compressor 11 in that order. At the same time, the refrigerant circuit is switched to one in which the refrigerant discharged from the compressor 11 circulates through the radiator 12, the second expansion valve 14b, the chiller 17, the second three-way valve 16b, the accumulator 18, and the suction port of the compressor 11 in that order.

[0119] The control device 50 also operates the indoor blower 15a. The control device 50 also operates the heat medium pump 31. The control device 50 also appropriately controls the operation of various controlled devices so that the temperature of the blown air becomes appropriate for cooling the air-conditioned space, and the temperature of the cooling target device 70 becomes appropriate.

[0120] Therefore, in the refrigerant circuit 10 in the third composite cooling mode, a vapor compression refrigeration cycle is configured in which the radiator 12 functions as a condenser, and the cooling evaporator 15 and the chiller 17 function as evaporators. The cooling evaporator 15 cools the blown air. The chiller 17 cools the heat medium.

[0121] In the heat medium circuit 30 in the third composite cooling mode, the heat medium flowing out of the heat medium passage of the chiller 17 is pumped to the coolant passage 70a of the device 70 to be cooled, as indicated by the dashed arrow in FIG.

[0122] As a result, in the refrigeration cycle apparatus 1 in the third composite cooling mode, the blown air cooled by the cooling evaporator 15 is blown into the space to be air-conditioned, thereby cooling the space to be air-conditioned. Also, the heat medium cooled by the chiller 17 flows through the cooling water passage 70a of the equipment to be cooled 70, thereby cooling the equipment to be cooled 70.

[0123] 6, the first path is indicated by a thick solid line, and the second path is indicated by a thick dashed line. In the third composite cooling mode, the first three-way valve 16a is switched to the first flow mode. Furthermore, in the third composite cooling mode, the second three-way valve 16b is switched to the second flow mode.

[0124] As described above, the refrigeration cycle device 1 of the present embodiment can perform comfortable cooling of the space to be air-conditioned and appropriate cooling of the equipment to be cooled by switching the operation mode.

[0125] Here, in a refrigeration cycle device equipped with a plurality of evaporators and accumulators like the refrigeration cycle device 1 of the present embodiment, if the refrigerant cannot flow into the accumulator 18 when the refrigerant circuit is switched, the surplus refrigerant cannot be stored. As a result, the refrigeration cycle device 1 cannot be operated stably, and the evaporator cannot exert its cooling capacity.

[0126] Furthermore, in a refrigeration cycle device having multiple evaporators for cooling multiple types of objects to be cooled, it becomes necessary to appropriately adjust the cooling capacity of each evaporator depending on the temperature conditions of each object to be cooled, etc.

[0127] In contrast, in the refrigeration cycle device 1 of the present embodiment, the accumulator 18 is disposed in at least one of the first path and the second path in any operation mode. Therefore, at least one of the refrigerant that has absorbed heat from the blown air in the cooling evaporator 15 and the refrigerant that has absorbed heat from the refrigerant in the cooling target device 70 in the chiller 17 can be made to flow into the accumulator 18.

[0128] In other words, in any operation mode of the refrigeration cycle device 1 of this embodiment, the first three-way valve 16a and the second three-way valve 16b switch the refrigerant circuit as follows: That is, the refrigerant circuit is switched so that at least one of the refrigerant that has absorbed heat from the blown air in the cooling evaporator 15 and the refrigerant that has absorbed heat from the cooling target device 70 in the chiller 17 can flow into the accumulator 18.

[0129] This allows excess refrigerant in the cycle to be stored in the accumulator 18 in any operation mode, so that the refrigeration cycle device 1 can be operated stably, and the cooling evaporator 15 and the chiller 17 can be made to reliably exert their cooling capacity.

[0130] Furthermore, in the refrigeration cycle device 1 of this embodiment, the first three-way valve 16a can switch between a first flow mode and a first bypass flow mode, and the second three-way valve 16b can switch between a second flow mode and a second bypass flow mode.

[0131] In other words, one of the first path and the second path can be switched to a path in which the energy passes through the accumulator 18, and the other path can be switched to a path in which the energy bypasses the accumulator 18.

[0132] According to this, like the first combined cooling mode, the refrigerant flowing out from the chiller 17 can be made to bypass the accumulator 18 and be sucked into the compressor 11. Also, like the second combined cooling mode, the refrigerant flowing out from the cooling evaporator 15 can be made to bypass the accumulator 18 and be sucked into the compressor 11. Therefore, it is possible to adjust the cooling capacity of both the evaporating parts of the cooling evaporator 15 and the chiller 17.

[0133] Furthermore, the flow rate of the refrigerant flowing through the accumulator 18 can be reduced to reduce the pressure loss that occurs when the refrigerant flows through the accumulator 18. This increases the pressure of the suctioned refrigerant and increases the discharge flow rate of the compressor 11, thereby increasing the cooling capacity exerted by the cooling evaporator 15 and the chiller 17. As a result, the coefficient of performance (COP) of the refrigerant circuit 10 can be improved.

[0134] That is, in the refrigeration cycle device 1 of the present embodiment, the evaporating parts, such as the cooling evaporator 15 and the chiller 17, can exhibit appropriate cooling capacity.

[0135] In the refrigeration cycle device 1 of this embodiment, as described in (a) the first cooling mode and (b) the second cooling mode, it is possible to cool only one of the blown air and the cooled target device 70. At this time, the first three-way valve 16a and the second three-way valve 16b switch the energy flow path so that heat possessed by either the blown air or the cooled target device 70 is transferred to the intake refrigerant via the accumulator 18.

[0136] In other words, the refrigeration cycle device 1 of this embodiment can execute an operation mode in which the refrigerant is supplied to one of the cooling evaporator 15 and the chiller 17, and is not supplied to the other of the cooling evaporator 15 and the chiller 17. At this time, the first three-way valve 16a and the second three-way valve 16b switch the refrigerant circuit so that the refrigerant flowing out from one of the evaporation parts of the cooling evaporator 15 and the chiller 17 flows into the accumulator 18.

[0137] This allows excess refrigerant in the cycle to be stored in the accumulator 18 even in an operation mode in which only one of the blown air and the cooling target device 70 is cooled. As a result, the refrigeration cycle device 1 can be operated stably, and the cooling evaporator 15 or the chiller 17 can reliably exert its cooling capacity.

[0138] Furthermore, in the refrigeration cycle device 1 of this embodiment, as described in (c-1) the first composite cooling mode and (c-2) the second composite cooling mode, both the blown air and the equipment to be cooled 70 can be cooled. At this time, the first three-way valve 16a and the second three-way valve 16b switch the energy flow path so that heat possessed by one of the blown air and the equipment to be cooled 70 is transferred to the intake refrigerant via the accumulator 18, and heat possessed by the other is transferred to the intake refrigerant by bypassing the accumulator 18.

[0139] In other words, in the refrigeration cycle apparatus 1 of the present embodiment, the first three-way valve 16a and the second three-way valve 16b can be switched to a refrigerant circuit in which the refrigerant flowing out of the cooling evaporator 15 flows into the accumulator 18, and at the same time, the refrigerant flowing out of the chiller 17 bypasses the accumulator 18 and is guided to the suction side of the compressor 11. Furthermore, the refrigerant flowing out of the chiller 17 flows into the accumulator 18, and at the same time, the refrigerant flowing out of the cooling evaporator 15 can be switched to a refrigerant circuit in which the refrigerant flowing out of the cooling evaporator 15 bypasses the accumulator 18 and is guided to the suction side of the compressor 11.

[0140] In addition, in the refrigeration cycle device 1 of this embodiment, as described in (c-1) the first composite cooling mode and (c-2) the second composite cooling mode, the first three-way valve 16a and the second three-way valve 16b guide the refrigerant that has a higher enthalpy and becomes a gas-phase refrigerant having a degree of superheat, out of the refrigerant on the outlet side of the air-conditioning evaporator 15 and the refrigerant on the outlet side of the chiller 17, to the suction side of the compressor, bypassing the accumulator 18.

[0141] Therefore, for the evaporator section where the enthalpy of the outlet side refrigerant is higher, the enthalpy difference obtained by subtracting the enthalpy of the inlet side refrigerant from the enthalpy of the outlet side refrigerant is increased, thereby increasing the cooling capacity. Furthermore, the flow rate of the refrigerant flowing through the accumulator 18 is reduced, thereby effectively reducing the pressure loss that occurs when the refrigerant flows through the accumulator 18.

[0142] Moreover, in the refrigeration cycle apparatus 1 of the present embodiment, as described in the (c-3) third combined cooling mode, both the blown air and the equipment to be cooled 70 can be cooled.

[0143] At this time, the first three-way valve 16a and the second three-way valve 16b allow both the refrigerant flowing out from the cooling evaporator 15 and the refrigerant flowing out from the chiller 17 to flow into the accumulator 18. Therefore, surplus refrigerant in the cycle can be stored in the accumulator 18. As a result, the refrigeration cycle device 1 can be operated stably, and the cooling evaporator 15 and the chiller 17 can be made to reliably exert their cooling capacity.

[0144] The refrigeration cycle apparatus 1a of the present embodiment may execute another operation mode in addition to the above-mentioned operation mode.

[0145] For example, in the first cooling mode, the operation of the first three-way valve 16a may be controlled so that a portion of the refrigerant flowing out from the cooling evaporator 15 flows into the accumulator 18 and the remaining refrigerant flows into the first bypass passage 19a. In this case, the operation of the first three-way valve 16a may be controlled so that the cooling evaporator 15 exerts an appropriate cooling capacity, the surplus refrigerant is appropriately stored in the accumulator 18, and the pressure loss occurring when the refrigerant flows through the accumulator 18 is reduced.

[0146] For example, in the second cooling mode, the operation of the second three-way valve 16b may be controlled so that a portion of the refrigerant flowing out from the chiller 17 flows into the accumulator 18 and the remaining refrigerant flows into the second bypass passage 19b. In this case, the operation of the second three-way valve 16b may be controlled so that the chiller 17 exerts an appropriate cooling capacity, the surplus refrigerant is appropriately stored in the accumulator 18, and the pressure loss that occurs when the refrigerant flows through the accumulator 18 is reduced.

[0147] For example, in the first composite cooling mode and the second composite cooling mode, the first three-way valve 16a and the second three-way valve 16b may switch the energy flow path so as to transfer at least a portion of the heat possessed by one of the blown air and the cooled equipment 70 through the accumulator 18, and to transfer at least a portion of the heat possessed by the other cooled object, bypassing the accumulator 18.

[0148] In other words, in the first composite cooling mode and the second composite cooling mode, the operation of the first three-way valve 16a may be controlled so that a portion of the refrigerant flowing out from the air-conditioning evaporator 15 flows into the accumulator 18 and the remaining refrigerant flows into the first bypass passage 19a. Also, in the first composite cooling mode and the second composite cooling mode, the operation of the second three-way valve 16b may be controlled so that a portion of the refrigerant flowing out from the chiller 17 flows into the accumulator 18 and the remaining refrigerant flows into the second bypass passage 19b.

[0149] More specifically, as a modification of the first combined cooling mode, the operation of the first three-way valve 16a is controlled so that a portion of the refrigerant flowing out from the cooling evaporator 15 flows into the accumulator 18 and the remaining refrigerant flows into the first bypass passage 19a. Furthermore, the operation of the second three-way valve 16b may be controlled so that the entire flow rate of the refrigerant flowing out from the chiller 17 flows into the second bypass passage 19b.

[0150] In this case, the operation of the first three-way valve 16a may be controlled so that the cooling evaporator 15 or chiller 17 exerts an appropriate cooling capacity, the surplus refrigerant is appropriately stored in the accumulator 18, and the pressure loss occurring when the refrigerant flows through the accumulator 18 is reduced. The modified example of the first combined cooling mode is effective when the cooling capacity of the heat medium required in the chiller 17 is higher than the cooling capacity required in the cooling evaporator 15.

[0151] Second embodiment In this embodiment, a refrigeration cycle apparatus 1a will be described. The refrigeration cycle apparatus 1a of this embodiment is applied to an air conditioner with an equipment cooling function similar to that of the first embodiment. As shown in the overall configuration diagram of FIG. 7, the refrigeration cycle apparatus 1a includes a refrigerant circuit 10a, a heat medium circuit 30a, a control device 50, and the like.

[0152] In the refrigerant circuit 10a, a first chiller 17a is used instead of the cooling evaporator 15. In the refrigerant circuit 10a, the refrigerant inlet side of the first chiller 17a is connected to the outlet of the first expansion valve 14a. The first chiller 17a is a first evaporation section that exchanges heat between the low-pressure refrigerant decompressed by the first expansion valve 14a and the heat medium circulating in the heat medium circuit 30a. In the first chiller 17a, the low-pressure refrigerant is evaporated to exert a heat absorption effect, thereby cooling the heat medium.

[0153] In the refrigerant circuit 10a, the refrigerant inlet side of the second chiller 17b is connected to the outlet of the second expansion valve 14b. The second chiller 17b is a second evaporation section that exchanges heat between the low-pressure refrigerant decompressed by the second expansion valve 14b and the heat medium circulating in the heat medium circuit 30a. The second chiller 17b evaporates the low-pressure refrigerant to exert a heat absorption effect, thereby cooling the heat medium.

[0154] The basic configuration of the first chiller 17a and the second chiller 17b is similar to that of the chiller 17 described in the first embodiment.

[0155] The refrigerant outlet of the first chiller 17a is connected to the inlet side of the accumulator 18. The refrigerant outlet of the second chiller 17b is connected to one inlet side of the third three-way joint 13c. The gas phase refrigerant outlet of the accumulator 18 is connected to the other inlet side of the third three-way joint 13c.

[0156] For this reason, in the refrigerant circuit 10a, the first three-way valve 16a, the second three-way valve 16b, the first bypass passage 19a, the second bypass passage 19b, etc. described in the first embodiment are eliminated. Furthermore, in the refrigerant circuit 10a, the refrigerant passage leading from the refrigerant outlet of the second chiller 17b to one inlet of the third three-way joint 13c becomes a bypass passage 19 that guides the refrigerant flowing out of the second chiller 17b to the suction port side of the compressor 11, bypassing the accumulator 18.

[0157] Next, the heat medium circuit 30a will be described. The heat medium circuit 30a is a circuit that circulates a heat medium that has absorbed at least one of the heat of the blown air and the heat of the target device 70 to be cooled. In other words, the heat medium circuit 30a is a circuit that circulates a heat medium for transporting the heat of the blown air and the heat of the target device 70 to be cooled.

[0158] The heat medium circuit 30a is connected to a first heat medium pump 31a, a second heat medium pump 31b, a first heat medium four-way valve 20a, a second heat medium four-way valve 20b, a cooler core 151, a cooling water passage 70a formed in the device to be cooled 70, a heat medium passage of the first chiller 17a, a heat medium passage of the second chiller 17b, etc.

[0159] The cooler core 151 is a heat exchange unit for cooling that exchanges heat between a heat medium cooled by at least one of the first chiller 17a and the second chiller 17b and the blown air blown from the indoor blower 15a, thereby cooling the blown air.

[0160] The first heat medium pump 31a is a heat medium pumping unit that pumps the heat medium flowing out from the cooler core 151 to one heat medium inlet side of the first heat medium four-way valve 20a. The second heat medium pump 31b is a heat medium pumping unit that pumps the heat medium flowing out from the coolant passage 70a of the cooled target device 70 to the other heat medium inlet side of the first heat medium four-way valve 20a.

[0161] The basic configuration of the first heat medium pump 31a and the second heat medium pump 31b is similar to that of the heat medium pump 31 described in the first embodiment.

[0162] The first heat medium four-way valve 20a has two heat medium inlets and two heat medium outlets. One of the heat medium outlets of the first heat medium four-way valve 20a is connected to the inlet side of the heat medium passage of the first chiller 17a. The other of the heat medium outlets of the first heat medium four-way valve 20a is connected to the inlet side of the heat medium passage of the second chiller 17b.

[0163] The first heat medium four-way valve 20a can allow the heat medium that has flowed into it to flow out from at least one of the heat medium outlets. The first heat medium four-way valve 20a can continuously adjust the flow rate ratio between the flow rate of the heat medium that flows out from one of the heat medium outlets to the first chiller 17a side and the flow rate of the heat medium that flows out from the other heat medium outlet to the second chiller 17b side.

[0164] The first heat medium four-way valve 20a allows the heat medium flowing out from the cooler core 151 to flow into the interior and to flow out to either the first chiller 17a side or the second chiller 17b side. At the same time, the first heat medium four-way valve 20a allows the heat medium flowing out from the cooling water passage 70a of the cooled device 70 to flow into the interior and to flow out to the other of the first chiller 17a side or the second chiller 17b side.

[0165] Furthermore, in the first heat medium four-way valve 20a, the heat medium flowing out from the cooler core 151 and the heat medium flowing out from the cooling water passage 70a of the cooled equipment 70 can be mixed and flowed to at least one of the first chiller 17a side and the second chiller 17b side.

[0166] The operation of the first heat medium four-way valve 20a is controlled by a control signal output from the control device 50. Such a heat medium four-way valve can be formed by combining an electric three-way valve and a solenoid valve.

[0167] One heat medium inlet side of the second heat medium four-way valve 20b is connected to the outlet of the heat medium passage of the first chiller 17a. The other heat medium inlet side of the second heat medium four-way valve 20b is connected to the outlet of the heat medium passage of the second chiller 17b. The basic configuration of the second heat medium four-way valve 20b is the same as that of the first heat medium four-way valve 20a.

[0168] One heat medium outlet of the second heat medium four-way valve 20b is connected to the heat medium inlet side of the cooler core 151. The other heat medium outlet of the second heat medium four-way valve 20b is connected to the inlet side of the coolant passage 70a of the device 70 to be cooled.

[0169] The second heat medium four-way valve 20b can cause the heat medium that has flowed into it to flow out from at least one of the heat medium outlets. The second heat medium four-way valve 20b can continuously adjust the flow rate ratio between the flow rate of the heat medium that flows out from one of the heat medium outlets to the cooler core 151 side and the flow rate of the heat medium that flows out from the other heat medium outlet to the coolant passage 70a side of the cooled target device 70.

[0170] The second heat medium four-way valve 20b allows the heat medium flowing out from the first chiller 17a to flow inside and to flow out to either the cooler core 151 side or the cooling water passage 70a side of the cooled target equipment 70. At the same time, the second heat medium four-way valve 20b allows the heat medium flowing out from the second chiller 17b to flow inside and to flow out to the other of the cooler core 151 side or the cooling water passage 70a side of the cooled target equipment 70.

[0171] Furthermore, in the second heat medium four-way valve 20b, the heat medium flowing out of the first chiller 17a and the heat medium flowing out of the second chiller 17b can be mixed and flowed to at least one of the cooler core 151 side and the cooling water passage 70a of the equipment to be cooled 70.

[0172] Therefore, the first heat medium four-way valve 20a and the second heat medium four-way valve 20b are a heat medium circuit switching unit that switches the heat medium circuit 30a.

[0173] Next, the control device 50 of the refrigeration cycle apparatus 1a will be described. In the control device 50, a heat medium circuit control unit 50c is configured to control the operation of the first heat medium four-way valve 20a and the second heat medium four-way valve 20b, which are heat medium circuit switching units. The rest of the configuration of the refrigeration cycle apparatus 1a is the same as that of the refrigeration cycle apparatus 1 described in the first embodiment.

[0174] Next, the operation of the refrigeration cycle device 1a of the present embodiment in the above configuration will be described. In the refrigeration cycle device 1a, various operation modes are switched in the same manner as in the first embodiment in order to cool the blown air and the cooling target device 70. The detailed operation of each operation mode will be described below.

[0175] (a) First cooling mode In the first cooling mode, the control device 50 controls the first expansion valve 14a to be in a throttled state and the second expansion valve 14b to be in a fully closed state.

[0176] Therefore, in the refrigerant circuit 10a in the first cooling mode, as shown by the solid arrow in Figure 8, the refrigerant discharged from the compressor 11 is switched to a refrigerant circuit in which it circulates through the radiator 12, the first expansion valve 14a, the first chiller 17a, the accumulator 18, and the suction port of the compressor 11 in that order.

[0177] The control device 50 also operates the first heat medium pump 31a. The control device 50 also controls the operation of the first heat medium four-way valve 20a so that the entire flow rate of the heat medium that has flowed in from the cooler core 151 side flows out to the first chiller 17a side. The control device 50 also controls the operation of the second heat medium four-way valve 20b so that the entire flow rate of the heat medium that has flowed in from the first chiller 17a side flows out to the cooler core 151 side.

[0178] For this reason, in the heat medium circuit 30a in the first cooling mode, as shown by the dashed arrow in FIG. 8, the heat medium pumped by the first heat medium pump 31a is switched to a heat medium circuit in which the heat medium circulates in the following order: the first heat medium four-way valve 20a, the heat medium passage of the first chiller 17a, the second heat medium four-way valve 20b, the cooler core 151, and the suction port of the first heat medium pump 31a.

[0179] The control device 50 also operates the indoor blower 15a. The control device 50 also appropriately controls the operation of various controlled devices so that the temperature of the blown air becomes an appropriate temperature for cooling the space to be air-conditioned.

[0180] Therefore, in the refrigerant circuit 10a in the first cooling mode, a vapor compression refrigeration cycle is configured in which the radiator 12 functions as a condenser and the first chiller 17a functions as an evaporator. In the first chiller 17a, the heat medium is cooled.

[0181] In the heat medium circuit 30a in the first cooling mode, the heat medium cooled in the first chiller 17a flows into the cooler core 151. In the cooler core 151, the blown air is cooled.

[0182] As a result, in the refrigeration cycle apparatus 1a in the first cooling mode, the blown air cooled by the cooler core 151 is blown out into the space to be air-conditioned, thereby realizing cooling of the space to be air-conditioned.

[0183] Here, in Fig. 8, the first path is indicated by a thick solid line. In the refrigeration cycle apparatus 1a, an accumulator 18 is disposed on the first path. The bypass passage 19 serves as the first bypass path. The first heat medium four-way valve 20a and the second heat medium four-way valve 20b serve as the first switching unit and the second switching unit. In the first cooling mode, the first heat medium four-way valve 20a and the second heat medium four-way valve 20b are switched to the first flow mode.

[0184] (b) Second cooling mode In the second cooling mode, the control device 50 controls the first expansion valve 14a to be in a throttled state and the second expansion valve 14b to be in a fully closed state.

[0185] Therefore, in the refrigerant circuit 10a in the first cooling mode, as in the first cooling mode, the refrigerant discharged from the compressor 11 is switched to a refrigerant circuit in which it circulates in the order of the radiator 12, the first expansion valve 14a, the first chiller 17a, the accumulator 18, and the suction port of the compressor 11, as shown by the solid arrow in Figure 9.

[0186] The control device 50 also operates the second heat medium pump 31b. The control device 50 also controls the operation of the first heat medium four-way valve 20a so that the entire flow rate of the heat medium that has flowed in from the cooling water passage 70a side of the cooled target device 70 flows out to the first chiller 17a side. The control device 50 also controls the operation of the second heat medium four-way valve 20b so that the entire flow rate of the heat medium that has flowed in from the first chiller 17a side flows out to the cooling water passage 70a side of the cooled target device 70.

[0187] For this reason, in the heat medium circuit 30a in the second cooling mode, as shown by the dashed arrow in FIG. 9, the heat medium pumped by the second heat medium pump 31b is switched to a heat medium circuit in which the heat medium circulates in this order through the first heat medium four-way valve 20a, the heat medium passage of the first chiller 17a, the second heat medium four-way valve 20b, the cooling water passage 70a of the cooled device 70, and the suction port of the second heat medium pump 31b.

[0188] Furthermore, the control device 50 appropriately controls the operation of various controlled devices so that the temperature of the cooling target device 70 becomes an appropriate temperature.

[0189] Therefore, in the refrigerant circuit 10a in the second cooling mode, a vapor compression refrigeration cycle is configured in which the radiator 12 functions as a condenser and the first chiller 17a functions as an evaporator. In the first chiller 17a, the heat medium is cooled.

[0190] In the heat medium circuit 30a in the second cooling mode, the heat medium cooled in the first chiller 17a flows into the coolant passage 70a of the device 70 to be cooled.

[0191] As a result, in the refrigeration cycle apparatus 1a in the second cooling mode, the heat medium cooled in the first chiller 17a flows through the cooling water passage 70a of the equipment 70 to be cooled, thereby cooling the equipment 70 to be cooled.

[0192] Here, in Fig. 9, the second path is indicated by a thick dashed line. In the refrigeration cycle apparatus 1a, an accumulator 18 is disposed on the second path. The bypass passage 19 also serves as the second bypass path. In the second cooling mode, the first heat medium four-way valve 20a and the second heat medium four-way valve 20b are switched to the second flow mode.

[0193] (c) Combined cooling mode The composite cooling modes of the refrigeration cycle apparatus 1a include (c-1) a first composite cooling mode and (c-2) a second composite cooling mode. In the composite cooling mode of the present embodiment, the circuit configuration of the heat medium circuit 30a is switched to select an operation mode such that the enthalpy of the refrigerant on the outlet side of the second chiller 17b becomes higher than the enthalpy of the refrigerant on the outlet side of the first chiller 17a, and the refrigerant on the outlet side of the second chiller 17b becomes a gas-phase refrigerant having a degree of superheat.

[0194] (c-1) First combined cooling mode In the refrigerant circuit 10a in the first composite cooling mode, the controller 50 places the first expansion valve 14a in a throttling state, and the second expansion valve 14b in a throttling state.

[0195] 10, the refrigerant discharged from the compressor 11 circulates through the radiator 12, the first expansion valve 14a, the first chiller 17a, the accumulator 18, and the suction port of the compressor 11 in that order. At the same time, the refrigerant circuit is switched to one in which the refrigerant discharged from the compressor 11 circulates through the radiator 12, the second expansion valve 14b, the second chiller 17b, and the suction port of the compressor 11 in that order.

[0196] The controller 50 also operates the first heat medium pump 31a and the second heat medium pump 31b.

[0197] In addition, the control device 50 controls the operation of the first heat medium four-way valve 20a so that the entire flow rate of the heat medium flowing in from the cooler core 151 side flows out to the first chiller 17a side, and at the same time, the entire flow rate of the heat medium flowing in from the cooling water passage 70a side of the cooled equipment 70 flows out to the second chiller 17b side.

[0198] In addition, the control device 50 controls the operation of the second heat medium four-way valve 20b so that the entire flow rate of the heat medium flowing in from the first chiller 17a side flows out to the cooler core 151 side, and at the same time, the entire flow rate of the heat medium flowing in from the second chiller 17b side flows out to the cooling water passage 70a side of the equipment to be cooled 70.

[0199] Therefore, in the heat medium circuit 30a in the first combined cooling mode, as shown by the dashed arrow in Fig. 10, the heat medium pumped by the first heat medium pump 31a is switched to a heat medium circuit in which the heat medium circulated from the first heat medium pump 31a circulates through the first heat medium four-way valve 20a, the heat medium passage of the first chiller 17a, the second heat medium four-way valve 20b, the cooler core 151, and the suction port of the first heat medium pump 31a in that order. At the same time, the heat medium pumped by the second heat medium pump 31b is switched to a heat medium circuit in which the heat medium circulated from the second heat medium pump 31b circulates through the first heat medium four-way valve 20a, the heat medium passage of the second chiller 17b, the second heat medium four-way valve 20b, the coolant passage 70a of the cooled device 70, and the suction port of the second heat medium pump 31b in that order.

[0200] The control device 50 also operates the indoor blower 15a. The control device 50 also appropriately controls the operation of various controlled devices so that the temperature of the blown air becomes appropriate for cooling the air-conditioned space and the temperature of the cooling target device 70 becomes appropriate.

[0201] Therefore, in the refrigerant circuit 10a in the first composite cooling mode, a vapor compression refrigeration cycle is configured in which the radiator 12 functions as a condenser and the first chiller 17a and the second chiller 17b function as evaporators. The first chiller 17a and the second chiller 17b each cool a heat medium.

[0202] 10, in the heat medium circuit 30a in the first combined cooling mode, the heat medium cooled in the first chiller 17a flows into the cooler core 151. In addition, the heat medium cooled in the second chiller 17b flows into the coolant passage 70a of the device 70 to be cooled.

[0203] As a result, in the refrigeration cycle apparatus 1a in the first composite cooling mode, the blown air cooled by the cooler core 151 is blown into the space to be air-conditioned, thereby cooling the space to be air-conditioned. Also, the heat medium cooled by the second chiller 17b flows through the cooling water passage 70a of the equipment to be cooled 70, thereby cooling the equipment to be cooled 70.

[0204] Here, in Fig. 10, the first path is indicated by a thick solid line, and the second path is indicated by a thick dashed line. In the first composite cooling mode, the first heat medium four-way valve 20a and the second heat medium four-way valve 20b are switched to the first flow mode and also to the second bypass flow mode.

[0205] In the first combined cooling mode, the refrigerant flowing out of the first chiller 17a flows into the accumulator 18, and the refrigerant flowing out of the second chiller 17b bypasses the accumulator 18 and is guided to the suction port side of the compressor 11.

[0206] As a result, in the first composite cooling mode, the enthalpy difference obtained by subtracting the enthalpy of the inlet side refrigerant from the enthalpy of the outlet side refrigerant of the second chiller 17b is increased, thereby increasing the cooling capacity of the second chiller 17b. In other words, the cooling capacity for cooling the target device 70 can be increased.

[0207] (c-2) Second composite cooling mode In the refrigerant circuit 10a in the second composite cooling mode, the controller 50 places the first expansion valve 14a in a throttling state, and the second expansion valve 14b in a throttling state.

[0208] Therefore, in the refrigerant circuit 10a in the second composite cooling mode, as in the first composite cooling mode, the refrigerant discharged from the compressor 11 circulates in the order of the radiator 12, the first expansion valve 14a, the first chiller 17a, the accumulator 18, and the suction port of the compressor 11, as shown by the solid arrows in Fig. 11. At the same time, the refrigerant circuit is switched to one in which the refrigerant discharged from the compressor 11 circulates in the order of the radiator 12, the second expansion valve 14b, the second chiller 17b, and the suction port of the compressor 11.

[0209] The controller 50 also operates the first heat medium pump 31a and the second heat medium pump 31b.

[0210] In addition, the control device 50 controls the operation of the first heat medium four-way valve 20a so that the entire flow rate of the heat medium flowing in from the cooler core 151 side flows out to the second chiller 17b side, and at the same time, the entire flow rate of the heat medium flowing in from the cooling water passage 70a side of the cooled equipment 70 flows out to the first chiller 17a side.

[0211] In addition, the control device 50 controls the operation of the second heat medium four-way valve 20b so that the entire flow rate of the heat medium flowing in from the first chiller 17a side flows out to the cooling water passage 70a side of the cooled equipment 70, and at the same time, the entire flow rate of the heat medium flowing in from the second chiller 17b side flows out to the cooler core 151 side.

[0212] Therefore, in the heat medium circuit 30a in the second combined cooling mode, as shown by the dashed arrow in Fig. 11, the heat medium pumped by the first heat medium pump 31a is switched to a heat medium circuit in which the heat medium circulated from the first heat medium pump 31a circulates through the first heat medium four-way valve 20a, the heat medium passage of the second chiller 17b, the second heat medium four-way valve 20b, the cooler core 151, and the suction port of the first heat medium pump 31a in that order. At the same time, the heat medium pumped by the second heat medium pump 31b is switched to a heat medium circuit in which the heat medium circulated from the second heat medium pump 31b circulates through the first heat medium four-way valve 20a, the heat medium passage of the first chiller 17a, the second heat medium four-way valve 20b, the coolant passage 70a of the cooled device 70, and the suction port of the second heat medium pump 31b in that order.

[0213] The control device 50 also operates the indoor blower 15a. The control device 50 also appropriately controls the operation of various controlled devices so that the temperature of the blown air becomes appropriate for cooling the air-conditioned space and the temperature of the cooling target device 70 becomes appropriate.

[0214] Therefore, in the refrigerant circuit 10a in the second composite cooling mode, a vapor compression refrigeration cycle is configured in which the radiator 12 functions as a condenser and the first chiller 17a and the second chiller 17b function as evaporators. The first chiller 17a and the second chiller 17b each cool a heat medium.

[0215] 11, in the heat medium circuit 30a in the second composite cooling mode, the heat medium cooled in the second chiller 17b flows into the cooler core 151. In addition, the heat medium cooled in the first chiller 17a flows into the coolant passage 70a of the device 70 to be cooled.

[0216] As a result, in the refrigeration cycle apparatus 1a in the second composite cooling mode, the blown air cooled by the cooler core 151 is blown into the space to be air-conditioned, thereby cooling the space to be air-conditioned. Also, the heat medium cooled by the first chiller 17a flows through the cooling water passage 70a of the equipment to be cooled 70, thereby cooling the equipment to be cooled 70.

[0217] Here, in Fig. 11, the first path is indicated by a thick solid line, and the second path is indicated by a thick dashed line. In the second composite cooling mode, the first heat medium four-way valve 20a and the second heat medium four-way valve 20b are switched to the first bypass flow mode and also to the second flow mode.

[0218] In the second combined cooling mode, the refrigerant flowing out of the first chiller 17a flows into the accumulator 18, and the refrigerant flowing out of the second chiller 17b bypasses the accumulator 18 and is guided to the suction port side of the compressor 11.

[0219] As a result, in the second composite cooling mode, the enthalpy difference obtained by subtracting the enthalpy of the inlet side refrigerant from the enthalpy of the outlet side refrigerant of the second chiller 17b is increased, thereby increasing the cooling capacity of the second chiller 17b. In other words, the cooling capacity for cooling the blown air can be increased.

[0220] As described above, the refrigeration cycle device 1 of the present embodiment can perform comfortable cooling of the space to be air-conditioned and appropriate cooling of the equipment to be cooled by switching the operation mode.

[0221] Furthermore, the refrigeration cycle apparatus 1a of the present embodiment can also obtain the same effects as the refrigeration cycle apparatus 1 described in the first embodiment. That is, the refrigeration cycle apparatus 1a of the present embodiment can also cause the evaporator to exhibit an appropriate cooling capacity.

[0222] More specifically, in the refrigeration cycle apparatus 1a of the present embodiment, the accumulator 18 is disposed in at least one of the first path and the second path in any operation mode. Therefore, in the first chiller 17a, the refrigerant that has absorbed heat from at least one of the blown air and the cooling target device 70 can be made to flow into the accumulator 18.

[0223] In other words, in the refrigeration cycle apparatus 1a of this embodiment, in any operation mode, the first heat medium four-way valve 20a and the second heat medium four-way valve 20b switch the refrigerant circuit as follows: That is, at least one of the heat medium that has absorbed heat from the blown air and the heat medium that has absorbed heat from the cooled target device 70 is switched to a heat medium circuit that exchanges heat with the refrigerant flowing through the first chiller 17a.

[0224] This allows excess refrigerant in the cycle to be stored in the accumulator 18 in any operation mode. As a result, the refrigeration cycle apparatus 1a can be operated stably, and the first chiller 17a and the second chiller 17b can be made to reliably exert their cooling capacity.

[0225] Furthermore, in the refrigeration cycle apparatus 1a of this embodiment, the first heat medium four-way valve 20a and the second heat medium four-way valve 20b can switch between a first flow mode and a first bypass flow mode. Similarly, the first heat medium four-way valve 20a and the second heat medium four-way valve 20b can switch between a second flow mode and a second bypass flow mode.

[0226] That is, one of the first path and the second path can be switched to a path in which energy passes through the accumulator 18, and the other can be switched to a path in which energy bypasses the accumulator 18. As a result, the cooling capacity of the second chiller 17b can be increased. Furthermore, the flow rate of the refrigerant flowing through the accumulator 18 can be reduced, thereby reducing the pressure loss that occurs when the refrigerant flows through the accumulator 18.

[0227] That is, in the refrigeration cycle apparatus 1a of this embodiment as well, it is possible to cause the evaporating parts such as the first chiller 17a and the second chiller 17b to exhibit appropriate cooling capacity.

[0228] In the refrigeration cycle apparatus 1a of this embodiment, as described in (a) the first cooling mode and (b) the second cooling mode, it is possible to cool only one of the blown air and the cooling target device 70. At this time, the first heat medium four-way valve 20a and the second heat medium four-way valve 20b switch the energy flow path so that the heat of either the blown air or the cooling target device 70 is transferred to the intake refrigerant via the accumulator 18.

[0229] In other words, in the refrigeration cycle apparatus 1a of the present embodiment, the heat medium circuit is switched so that the heat medium that has absorbed either the heat of the blown air or the heat of the cooled target device 70 flows into the first chiller 17a.

[0230] This allows excess refrigerant in the cycle to be stored in the accumulator 18 even in an operation mode in which only one of the blown air and the cooling target device 70 is cooled. As a result, the refrigeration cycle apparatus 1a can be stably operated, and the first chiller 17a can reliably exert its cooling capacity.

[0231] Furthermore, in the refrigeration cycle apparatus 1a of this embodiment, as described in (c-1) the first composite cooling mode and (c-2) the second composite cooling mode, both the blown air and the cooled target device 70 can be cooled. At this time, the first heat medium four-way valve 20a and the second heat medium four-way valve 20b switch the energy flow path so that heat possessed by one of the blown air and the cooled target device 70 is transferred to the intake refrigerant via the accumulator 18, and heat possessed by the other is transferred to the intake refrigerant by bypassing the accumulator 18.

[0232] In other words, in the refrigeration cycle apparatus 1a of this embodiment, the first heat medium four-way valve 20a and the second heat medium four-way valve 20b can be switched to a heat medium circuit that exchanges heat between the heat medium that has absorbed the heat of the blown air and the refrigerant flowing through the first chiller 17a and the heat medium that has absorbed the heat of the cooled target device 70 and the refrigerant flowing through the second chiller 17b. Furthermore, the heat medium that has absorbed the heat of the cooled target device 70 and the refrigerant flowing through the first chiller 17a can be switched to a heat medium circuit that exchanges heat between the heat medium that has absorbed the heat of the blown air and the refrigerant flowing through the second chiller 17b.

[0233] Furthermore, in the refrigeration cycle apparatus 1a of this embodiment, as described in (c-1) the first composite cooling mode and (c-2) the second composite cooling mode, the operation mode of the first heat medium four-way valve 20a and the second heat medium four-way valve 20b is selected such that the enthalpy of the refrigerant on the outlet side of the second chiller 17b is higher than the enthalpy of the refrigerant on the outlet side of the first chiller 17a, and the refrigerant on the outlet side of the second chiller 17b becomes a gas-phase refrigerant having a degree of superheat.

[0234] As a result, for second chiller 17b, the enthalpy difference obtained by subtracting the enthalpy of the inlet side refrigerant from the enthalpy of the outlet side refrigerant is increased, thereby increasing the cooling capacity. Furthermore, the flow rate of the refrigerant flowing through accumulator 18 is reduced, thereby effectively reducing the pressure loss that occurs when the refrigerant flows through accumulator 18.

[0235] The refrigeration cycle apparatus 1a of the present embodiment may execute another operation mode in addition to the above-mentioned operation mode.

[0236] For example, an operation mode may be executed in which the first heat medium four-way valve 20a and the second heat medium four-way valve 20b switch to a heat medium circuit in which the entire flow rate of the heat medium flowing out from the cooler core 151 and the coolant passage 70a of the cooled target equipment 70 flows into the first chiller 17a, and the heat medium flowing out from the first chiller 17a flows into both the cooler core 151 and the coolant passage 70a of the cooled target equipment 70. In this case, the second expansion valve 14b may be fully closed.

[0237] For example, an operation mode may be executed in which the first heat medium four-way valve 20a and the second heat medium four-way valve 20b cause the heat medium flowing out of the cooler core 151 to flow into both the first chiller 17a and the second chiller 17b, and switch to a circuit configuration in which the total flow rate of the heat medium flowing out of the first chiller 17a and the second chiller 17b flows into the cooler core 151. At this time, the first expansion valve 14a may be in a throttling state, and the second expansion valve 14b may be in a throttling state.

[0238] For example, an operation mode may be executed in which the first heat medium four-way valve 20a and the second heat medium four-way valve 20b cause the heat medium flowing out from the cooling water passage 70a of the cooled target device 70 to flow into both the first chiller 17a and the second chiller 17b, and switch to a circuit configuration in which the total flow rate of the heat medium flowing out from the first chiller 17a and the second chiller 17b flows into the cooling water passage 70a of the cooled target device 70. In this case, the first expansion valve 14a may be in a throttling state, and the second expansion valve 14b may be in a throttling state.

[0239] Even in the above operation mode, the refrigerant flowing out of the first chiller 17a can be caused to flow into the accumulator 18, so that the accumulator 18 can store surplus refrigerant in the cycle.

[0240] Furthermore, an operation mode can be executed in which the first heat medium four-way valve 20a and the second heat medium four-way valve 20b switch to a heat medium circuit in which the total flow rate of the heat medium flowing out from the cooler core 151 and the cooling water passage 70a of the cooled equipment 70 flows into the second chiller 17b, and the heat medium flowing out from the second chiller 17b flows into both the cooler core 151 and the cooling water passage 70a of the cooled equipment 70.

[0241] Third embodiment In the refrigeration cycle apparatus 1 of the third embodiment, the first three-way valve 16a and the first bypass passage 19a, etc. are eliminated from the first embodiment, as shown in the overall configuration diagram of Fig. 12. In the refrigeration cycle apparatus 1 of the present embodiment, the operations of (a) the first cooling mode, (b) the second cooling mode, (c-1) the first composite cooling mode, and (c-3) the third composite cooling mode described in the first embodiment can be performed.

[0242] Other configurations and operations are the same as those of the first embodiment. Therefore, in the refrigeration cycle device 1 of this embodiment as well, at least one of the refrigerant that absorbs heat from the blown air in the cooling evaporator 15 and the refrigerant that absorbs heat from the refrigerant in the equipment to be cooled 70 in the chiller 17 can be made to flow into the accumulator 18. Then, the accumulator 18 can store surplus refrigerant in the cycle.

[0243] As a result, the refrigeration cycle apparatus 1 can be stably operated, and the cooling evaporator 15 and the chiller 17 can be made to reliably exert their cooling capacity. Also in the first combined cooling mode of this embodiment, as in the first embodiment, the cooling capacity of the chiller 17 can be increased. Furthermore, the pressure loss that occurs when the refrigerant flows through the accumulator 18 can be reduced.

[0244] (Fourth embodiment) In the refrigeration cycle apparatus 1 of the fourth embodiment, the second three-way valve 16b and the second bypass passage 19b are eliminated from the first embodiment, as shown in the overall configuration diagram of Fig. 13. In the refrigeration cycle apparatus 1 of this embodiment, the operations of (a) the first cooling mode, (b) the second cooling mode, (c-2) the second composite cooling mode, and (c-3) the third composite cooling mode described in the first embodiment can be performed.

[0245] Other configurations and operations are the same as those of the first embodiment. Therefore, in the refrigeration cycle device 1 of this embodiment as well, at least one of the refrigerant that absorbs heat from the blown air in the cooling evaporator 15 and the refrigerant that absorbs heat from the refrigerant in the equipment to be cooled 70 in the chiller 17 can be made to flow into the accumulator 18. Then, the accumulator 18 can store surplus refrigerant in the cycle.

[0246] As a result, the refrigeration cycle apparatus 1 can be stably operated, and the cooling evaporator 15 and the chiller 17 can be made to reliably exert their cooling capacity. Also in the second combined cooling mode of this embodiment, as in the first embodiment, the cooling capacity of the cooling evaporator 15 can be increased. Furthermore, the pressure loss that occurs when the refrigerant flows through the accumulator 18 can be reduced.

[0247] Fifth embodiment In the refrigeration cycle apparatus 1a of the fifth embodiment, a first three-way valve 16a and a second three-way valve 16b, which are refrigerant circuit switching units, are added to the second embodiment, as shown in the overall configuration diagram of Fig. 14. Furthermore, in the refrigeration cycle apparatus 1a of the present embodiment, a first bypass passage 19a and a second bypass passage 19b are provided as bypass passages.

[0248] In the refrigeration cycle device 1a of this embodiment, as described in the second embodiment, the first chiller 17a is the first evaporator and the second chiller 17b is the second evaporator, and (a) the first cooling mode, (b) the second cooling mode, (c-1) the first composite cooling mode, and (c-2) the second composite cooling mode can be executed. Therefore, the same effects as those of the refrigeration cycle device 1a of the second embodiment can be obtained.

[0249] Furthermore, the second chiller 17b can be used as a first evaporator and the first chiller 17a can be used as a second evaporator to execute operating modes corresponding to (a) the first cooling mode, (b) the second cooling mode, (c-1) the first composite cooling mode, and (c-2) the second composite cooling mode.

[0250] This allows for greater freedom in selecting the operation mode compared to the second embodiment. In other words, when the heat exchange performance of the first chiller 17a and the second chiller 17b is different, an appropriate evaporator can be selected and used. Then, the refrigerant flowing out of the selected appropriate evaporator can be made to flow into the accumulator 18.

[0251] Sixth embodiment In this embodiment, as shown in the overall configuration diagram of Fig. 15, an example in which a bypass-side pressure reducing valve 14c is added to the refrigeration cycle apparatus 1 described in the third embodiment will be described. The bypass-side pressure reducing valve 14c is disposed in the second bypass passage 19b. Therefore, the bypass-side pressure reducing valve 14c is a bypass-side pressure reducing part that reduces the pressure of the refrigerant flowing through the bypass passage which is a bypass route.

[0252] The bypass side pressure reducing valve 14c has a basic configuration similar to that of the first expansion valve 14a etc. Furthermore, the bypass side pressure reducing valve 14c has a full opening function that functions simply as a refrigerant passage by fully opening the throttling degree and without exerting almost any refrigerant pressure reducing action or flow rate regulating action.

[0253] In the control device 50 of this embodiment, a configuration for controlling the operation of the bypass side pressure reducing valve 14c, which is a bypass side pressure reducing section, is a bypass side pressure reducing control section 50d. The other configurations of the refrigeration cycle device 1 are the same as those of the third embodiment.

[0254] Next, the operation of the refrigeration cycle device 1 of this embodiment in the above configuration will be described. In the refrigeration cycle device 1 of this embodiment, by fully opening the bypass side pressure reducing valve 14c, it is possible to perform operations in (a) the first cooling mode, (b) the second cooling mode, (c-1) the first composite cooling mode, and (c-3) the third composite cooling mode in exactly the same way as in the third embodiment. Therefore, it is possible to obtain the same effects as in the third embodiment.

[0255] Here, in the first composite cooling mode, as described in the third embodiment and the like, the degree of superheat of the refrigerant on the outlet side of the chiller 17 can be increased to increase the cooling capacity of the chiller 17. On the other hand, if the degree of superheat of the refrigerant on the outlet side of the chiller 17 is unnecessarily increased, the discharge refrigerant temperature Td will increase unnecessarily, which may adversely affect the durable life of the compressor 11.

[0256] Therefore, in the first composite cooling mode of this embodiment, the controller 50 controls the operation of the second expansion valve 14b and the bypass side pressure reducing valve 14c so that the discharge refrigerant temperature Td is equal to or lower than a predetermined reference discharge refrigerant temperature KTd. Furthermore, in this embodiment, the maximum allowable temperature determined based on the durability of the compressor 11 is used as the reference discharge refrigerant temperature KTd.

[0257] The first composite cooling mode of this embodiment will be described in detail with reference to the Mollier diagrams of Figures 16 and 17. First, the Mollier diagram of Figure 16 shows changes in the state of the refrigerant in a comparative operation mode. The comparative operation mode is the first composite cooling mode executed under operating conditions in which the bypass side pressure reducing valve 14c is fully open and the discharge refrigerant temperature Td exceeds the reference discharge refrigerant temperature KTd.

[0258] In the comparative operation mode, the discharged refrigerant (point a1 in FIG. 16) discharged from the compressor 11 flows into the radiator 12. The discharged refrigerant that flows into the radiator 12 exchanges heat with the outside air and dissipates heat (from point a1 to point b1 in FIG. 16). The flow of the refrigerant that flows out of the radiator 12 flows into the first three-way joint 13a and is branched.

[0259] One of the refrigerant branches at the first three-way joint 13a flows into the first expansion valve 14a and is depressurized (from point b1 to point c1 in FIG. 16). The refrigerant depressurized at the first expansion valve 14a flows into the cooling evaporator 15. The refrigerant that flows into the cooling evaporator 15 absorbs heat from the blown air and evaporates (from point c1 to point d1 in FIG. 16).

[0260] The refrigerant flowing out of the cooling evaporator 15 flows into the accumulator 18. Therefore, the refrigerant on the outlet side of the cooling evaporator 15 becomes saturated gas phase refrigerant.

[0261] The other refrigerant branched at the first three-way joint 13a flows into the second expansion valve 14b and is depressurized (from point b1 to point e1 in FIG. 16). The refrigerant depressurized at the second expansion valve 14b flows into the chiller 17. The refrigerant that flows into the chiller 17 absorbs heat from the heat medium and evaporates (from point e1 to point f1 in FIG. 16).

[0262] In the chiller 17, the enthalpy is increased until the refrigerant reaches a temperature equivalent to the heat medium temperature TW. Therefore, the refrigerant on the outlet side of the chiller 17 becomes a gas-phase refrigerant having a degree of superheat. The refrigerant flowing out of the chiller 17 flows into the bypass side pressure reducing valve 14c, which is fully open.

[0263] The flow of the refrigerant flowing out from the accumulator 18 and the flow of the refrigerant flowing out from the bypass side pressure reducing valve 14c join together at the third three-way joint 13c (from point d1 to point g1 in FIG. 16, and from point f1 to point g1 in FIG. 16). The refrigerant flowing out from the third three-way joint 13c (point g1 in FIG. 16) is sucked into the compressor 11 and compressed again.

[0264] In the comparative operation mode, the degree of superheat of the refrigerant on the outlet side of the chiller 17 increases with an increase in the temperature of the heat medium exchanging heat with the refrigerant in the chiller 17. This causes the degree of superheat of the gas-phase refrigerant (point g1 in FIG. 16) flowing out from the third three-way joint 13c to become unnecessarily high, and as shown in FIG. 16, the discharge refrigerant temperature Td exceeds the reference discharge refrigerant temperature KTd. As a result, it may not be possible to protect the compressor 11.

[0265] In contrast, in the first composite cooling mode of this embodiment, the controller 50 controls the operation of the second expansion valve 14b and the bypass side pressure reducing valve 14c so that the discharge refrigerant temperature Td becomes equal to or lower than the reference discharge refrigerant temperature KTd. As a result, the state of the refrigerant changes as shown in the Mollier diagram of Fig. 17. In Fig. 17, the state of the refrigerant at the points equivalent in the cycle configuration to those in the Mollier diagram of Fig. 16 are indicated by the same reference characters (alphabet) as in Fig. 16, but the subscripts (numbers) have been changed.

[0266] More specifically, in the first composite cooling mode of the present embodiment, the control device 50 increases the throttle opening of the second expansion valve 14b and decreases the throttle opening of the bypass side pressure reducing valve 14c more than in the comparative operation mode. Therefore, in the first composite cooling mode, the pressure of the refrigerant decompressed by the second expansion valve 14b (to point e2 in FIG. 17) becomes higher than in the comparative operation mode.

[0267] The refrigerant decompressed by the second expansion valve 14b flows into the chiller 17. The refrigerant that has flowed into the chiller 17 absorbs heat from the heat medium and evaporates (from point e2 to point f21 in FIG. 17).

[0268] In the chiller 17, the enthalpy is increased until the refrigerant reaches a temperature equivalent to the heat medium temperature TW. Therefore, the refrigerant on the outlet side of the chiller 17 becomes a gas-phase refrigerant having a degree of superheat. In the first combined cooling mode, the pressure of the refrigerant on the outlet side of the chiller 17 is higher than in the comparative operation mode, so the degree of superheat of the refrigerant on the outlet side of the chiller 17 is lower than in the comparative operation mode.

[0269] The refrigerant flowing out from the chiller 17 flows into the bypass side pressure reducing valve 14c and is reduced in pressure (from point f21 to point f22 in FIG. 17).

[0270] The flow of the refrigerant flowing out from the accumulator 18 and the flow of the refrigerant flowing out from the bypass side pressure reducing valve 14c join together at the third three-way joint 13c (from point d2 to point g2 in FIG. 17, and from point f22 to point g2 in FIG. 17). The refrigerant flowing out from the third three-way joint 13c (point g2 in FIG. 17) is sucked into the compressor 11 and compressed again.

[0271] In the first composite cooling mode, the degree of superheat of the refrigerant on the outlet side of the chiller 17 is lower than in the comparative operation mode, so the degree of superheat of the refrigerant flowing out of the third three-way joint 13c (point g2 in FIG. 17) is also lower than in the comparative operation mode. This makes it possible to make the discharge refrigerant temperature Td (the temperature at point a2 in FIG. 17) equal to or lower than the reference discharge refrigerant temperature KTd. As a result, it is possible to protect the compressor 11.

[0272] Of course, when the temperature of the heat medium exchanging heat with the refrigerant in the chiller 17 is relatively low and the discharge refrigerant temperature Td does not exceed the reference discharge refrigerant temperature KTd, the bypass side pressure reducing valve 14c can be fully opened to execute the first composite cooling mode.

[0273] The present disclosure is not limited to the above-described embodiment, and various modifications can be made as follows without departing from the spirit and scope of the present disclosure.

[0274] The refrigeration cycle apparatus 1, 1a described in the above embodiment may be applied to a vehicle air conditioner. In this case, the first object to be cooled may be the ventilation air blown into the vehicle cabin. The second object to be cooled may be a battery or other in-vehicle equipment.

[0275] The configuration of the refrigeration cycle apparatus according to the present disclosure is not limited to the configurations disclosed in the above-described embodiments.

[0276] In the above-described first embodiment, an example in which the chiller 17 that exchanges heat between the refrigerant and the heat medium is adopted as the second evaporator has been described, but the present invention is not limited thereto. For example, a cooling evaporator that exchanges heat between the refrigerant and the cooling blown air blown toward the second object to be cooled may be adopted as the second evaporator. In addition, when the chiller 17 is adopted as the second evaporator, a cooling heat exchanger (i.e., a cooler core) that exchanges heat between the heat medium cooled by the chiller 17 and the blown air blown toward the second object to be cooled may be adopted.

[0277] The refrigeration cycle device may further include a receiver in addition to the accumulator 18. The receiver is a high-pressure side gas-liquid separator that separates the refrigerant flowing out from the radiator 12 into gas and liquid and stores a part of the separated refrigerant as excess refrigerant for the cycle. In addition to the operation modes described in the above embodiment, there may be an operation mode that switches to a refrigerant circuit that stores the excess refrigerant in the receiver instead of the accumulator 18.

[0278] In the sixth embodiment, the bypass side pressure reducing valve 14c, which is a variable throttle mechanism, is used as the bypass side pressure reducing portion, but the present invention is not limited to this. The bypass side pressure reducing portion may be a fixed throttle. Specifically, an orifice, a capillary tube, a refrigerant pipe having a smaller diameter than other refrigerant pipes, or the like may be used as the bypass side pressure reducing portion.

[0279] Furthermore, the group of control sensors connected to the input side of the control device 50 is not limited to the detection units disclosed in the above embodiment. Various detection units may be added as necessary.

[0280] In the above embodiment, the refrigerant circuit 10, 10a constituting the vapor compression refrigeration cycle is refrigerated using R1234yf, but the present invention is not limited thereto. For example, R134a, R600a, R410A, R404A, R32, R407C, etc. may be used. Alternatively, a mixed refrigerant of a mixture of a plurality of these refrigerants may be used. Furthermore, carbon dioxide may be used as the refrigerant to constitute a supercritical refrigeration cycle in which the high-pressure side refrigerant pressure is equal to or higher than the critical pressure of the refrigerant.

[0281] In addition, although an example in which an ethylene glycol aqueous solution is used as the heat medium and the high-temperature side heat medium in the above embodiment has been described, the present invention is not limited to this. For example, dimethylpolysiloxane, a solution containing nanofluid, antifreeze, a water-based liquid refrigerant containing alcohol, a liquid medium containing oil, etc. may be used as the high-temperature side heat medium and the heat medium.

[0282] The control aspects of the refrigeration cycle apparatus according to the present disclosure are not limited to the control aspects disclosed in the above-described embodiments.

[0283] In the above-described embodiment (c-1) the first composite cooling mode and (c-2) the second composite cooling mode, an example has been described in which, of the outlet side refrigerant of the first evaporator section and the outlet side refrigerant of the second evaporator section, the refrigerant that has a higher enthalpy and becomes a gas phase refrigerant with a degree of superheat is guided to the suction side of the compressor 11 by bypassing the accumulator 18, but this is not limiting.

[0284] For example, in the (c-1) first composite cooling mode and (c-2) second composite cooling mode of the first embodiment, the intake temperature of the blown air exchanging heat with the refrigerant in the air-conditioning evaporator 15 may be compared with the heat medium temperature TW, and the refrigerant flowing out from the evaporation section into which the higher temperature flows may be guided to the intake side of the compressor 11, bypassing the accumulator 18.

[0285] In the (c-1) first combined cooling mode and (c-2) second combined cooling mode of the second embodiment, the first heat medium temperature TW1 and the second heat medium temperature TW2 are compared, and the refrigerant flowing out of the evaporator into which the higher one flows may be guided to the suction port side of the compressor 11 by bypassing the accumulator 18. The first heat medium temperature TW1 is the temperature of the heat medium flowing into the first chiller 17a. The second heat medium temperature TW2 is the temperature of the heat medium flowing into the second chiller 17b.

[0286] In other words, the refrigerant flowing out from the evaporator section where the superheat degree of the outlet side refrigerant is more likely to be high may be guided to the suction port side of the compressor 11 by bypassing the accumulator 18 .

[0287] For example, the refrigerant flowing out of the evaporator having the greater flow rate of the refrigerant among the first and second evaporators may be guided to the suction port side of the compressor 11, bypassing the accumulator 18. This effectively reduces the pressure loss that occurs when the refrigerant flows through the accumulator 18. As a result, the pressure of the suctioned refrigerant is increased, and the discharge flow rate of the compressor 11 can be increased.

[0288] In the sixth embodiment, the operation of the bypass pressure reducing valve 14c is controlled so that the discharge refrigerant temperature Td is equal to or lower than the reference discharge refrigerant temperature KTd. However, the present invention is not limited to this. For example, the operation of the bypass pressure reducing valve 14c may be controlled so that the superheat degree SH of the suction refrigerant is equal to or lower than a predetermined reference superheat degree KSH.

[0289] The means disclosed in each of the above-described embodiments may be appropriately combined within a practicable range.

[0290] For example, the bypass side pressure reducing valve 14c described in the sixth embodiment may be applied to the other embodiments.

[0291] When applied to the refrigeration cycle apparatus 1 described in the first embodiment, the bypass side pressure reducing valve 14c may be disposed in the first bypass passage 19a, and control similar to that of the first composite cooling mode of the sixth embodiment may be performed in the second composite cooling mode. Furthermore, the bypass side pressure reducing valve 14c may be disposed in the second bypass passage 19b, and control similar to that of the first composite cooling mode of the sixth embodiment may be performed in the first composite cooling mode.

[0292] When applied to the refrigeration cycle apparatus 1a described in the second embodiment, the bypass side pressure reducing valve 14c may be disposed in the bypass passage 19, and control similar to that in the first composite cooling mode of the sixth embodiment may be performed in the first composite cooling mode and the second composite cooling mode.

[0293] Although the present disclosure has been described based on the embodiment, it is understood that the present disclosure is not limited to the embodiment or structure. The present disclosure also includes various modifications and modifications within the equivalent range. In addition, various combinations and forms, and other combinations and forms including only one element, more than one element, or less than one element, are also within the scope and concept of the present disclosure.

Claims

1. a first evaporator section (15, 17a) and a second evaporator section (17, 17b) for evaporating a refrigerant circulating through a refrigerant circuit (10); an accumulator (18) that separates the refrigerant flowing out from at least one of the first evaporation section and the second evaporation section into gas and liquid and stores an excess refrigerant; a compressor (11) that draws in and compresses the gas phase refrigerant separated in the accumulator, A refrigeration cycle apparatus in which the first evaporation section and the second evaporation section are connected in parallel with respect to a flow of the refrigerant, When a first path is defined as an energy flow path through which heat of a first object to be cooled moves to the intake refrigerant sucked into the compressor via at least one of the first evaporator and the second evaporator, and a second path is defined as an energy flow path through which heat of a second object to be cooled moves to the intake refrigerant via at least one of the first evaporator and the second evaporator, the accumulator is disposed in at least one of the first path and the second path; When the accumulator is disposed on the first path, a first bypass path (19, 19a) for transferring heat of the first object to be cooled by bypassing the accumulator; a first switching unit (16a, 20a, 20b) capable of switching between a first flow mode in which heat of the first object to be cooled is transferred via the accumulator and a first bypass flow mode in which the heat of the first object to be cooled is transferred via the first bypass path, When the accumulator is disposed on the second path, a second bypass path (19, 19b) for transferring heat of the second object to be cooled by bypassing the accumulator; and a second switching unit (16b, 20a, 20b) capable of switching between a second flow mode in which the heat of the second object to be cooled is transferred through the accumulator, and a second bypass flow mode in which the heat of the second object to be cooled is transferred through the second bypass path.

2. 2. The refrigeration cycle apparatus according to claim 1, wherein, when cooling one of the first object to be cooled and the second object to be cooled, the first switching unit and the second switching unit are switchable so that heat possessed by the one of the objects to be cooled is transferred via the accumulator.

3. 3. The refrigeration cycle device according to claim 1 or 2, wherein, when cooling both the first object to be cooled and the second object to be cooled, the first switching unit and the second switching unit are switchable to transfer at least a portion of the heat of one of the first object to be cooled and the second object to be cooled through the accumulator and to transfer at least a portion of the heat of the other object to be cooled by bypassing the accumulator.

4. 4. The refrigeration cycle device according to claim 3, wherein the first switching unit and the second switching unit switch the energy flow path, so that one of the outlet side refrigerant of the first evaporator and the outlet side refrigerant of the second evaporator, which has a higher enthalpy and becomes a gas phase refrigerant having a degree of superheat, bypasses the accumulator and is guided to the suction side of the compressor.

5. 4. The refrigeration cycle device according to claim 3, wherein the first switching unit and the second switching unit switch the energy flow path, so that the refrigerant flowing out of one of the first evaporation unit and the second evaporation unit, which has a larger flow rate of the refrigerant circulating therethrough, bypasses the accumulator and is guided to the suction port side of the compressor.

6. the first bypass path and the second bypass path are paths through which the refrigerant flows, 6. The refrigeration cycle apparatus according to claim 1, wherein at least one of the first bypass path and the second bypass path is provided with a bypass side pressure reduction section (14c) that reduces the pressure of the refrigerant.

7. A bypass side pressure reduction control unit (50d) for controlling operation of the bypass side pressure reduction unit, 7. The refrigeration cycle apparatus according to claim 6, wherein the bypass-side pressure reduction control unit controls operation of the bypass-side pressure reduction unit so that a discharge refrigerant temperature (Td), which is a temperature of the refrigerant discharged from the compressor, is equal to or lower than a predetermined reference discharge refrigerant temperature (KTd).

8. 8. The refrigeration cycle device according to claim 1, wherein the first switching unit and the second switching unit are refrigerant circuit switching units (16a, 16b) that switch the first path and the second path by switching the refrigerant circuit.

9. a heat medium circuit that circulates a heat medium that transfers heat of the first object to be cooled and heat of the second object to be cooled, 8. The refrigeration cycle apparatus according to claim 1, wherein the first switching unit and the second switching unit are heat medium circuit switching units (20a, 20b) that switch the first path and the second path by switching the heat medium circuit.

10. a first evaporator section (15) and a second evaporator section (17) for evaporating a refrigerant circulating through a refrigerant circuit (10); an accumulator (18) that separates the refrigerant flowing out from at least one of the first evaporation section and the second evaporation section into gas and liquid and stores an excess refrigerant; a compressor (11) that draws in and compresses the gas phase refrigerant separated in the accumulator, A refrigeration cycle apparatus in which the first evaporation section and the second evaporation section are connected in parallel with respect to a flow of the refrigerant, a bypass passage (19a, 19b) that guides at least one of the refrigerant flowing out from the first evaporation section and the refrigerant flowing out from the second evaporation section to a suction port side of the compressor, bypassing the accumulator; a refrigerant circuit switching unit (16a, 16b) that switches to a refrigerant circuit that causes at least one of the refrigerant flowing out of the first evaporation unit and the refrigerant flowing out of the second evaporation unit to flow into the accumulator.

11. The refrigerant circuit switching unit is a refrigerant circuit that causes the refrigerant flowing out of the first evaporation portion to flow into the accumulator and simultaneously causes the refrigerant flowing out of the second evaporation portion to flow into the bypass passage; a refrigerant circuit that causes the refrigerant flowing out of the second evaporation portion to flow into the accumulator and, at the same time, causes the refrigerant flowing out of the first evaporation portion to flow into the bypass passage.

12. a first evaporator section (17a) and a second evaporator section (17b) for evaporating a refrigerant circulating through a refrigerant circuit (10); an accumulator (18) that separates the refrigerant flowing out from the first evaporation section into gas and liquid and stores excess refrigerant; a compressor (11) that draws in and compresses the gas phase refrigerant separated in the accumulator; a bypass passage (19) that guides the refrigerant flowing out from the second evaporation section to a suction port side of the compressor by bypassing the accumulator, A refrigeration cycle apparatus in which the first evaporation section and the second evaporation section are connected in parallel with respect to a flow of the refrigerant, a heat medium circuit (30a) for circulating a heat medium for transporting heat of the first object to be cooled and heat of the second object to be cooled; a heat medium circuit switching unit (20a, 20b) that switches the heat medium that has absorbed at least one of the heat of the first object to be cooled and the heat of the second object to be cooled to a heat medium circuit that exchanges heat with the refrigerant circulating through the first evaporator.

13. The heat medium circuit switching unit is a heat medium circuit for exchanging heat between the heat medium that has absorbed heat from the first object to be cooled and the refrigerant that flows through the first evaporator, and at the same time, exchanging heat between the heat medium that has absorbed heat from the second object to be cooled and the refrigerant that flows through the second evaporator; 13. The refrigeration cycle device according to claim 12, wherein the heat medium is capable of heat exchanging with the refrigerant flowing through the second evaporator while the heat medium is capable of heat exchanging with the refrigerant flowing through the first evaporator.

14. The refrigeration cycle apparatus according to any one of claims 10 to 13, further comprising a bypass side pressure reducing section (14c) for reducing the pressure of the refrigerant flowing through the bypass passage.

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