Compressor module

Abstract

To suppress occurrence of liquid compression at re-operation of a compressor.SOLUTION: A compressor module includes evaporators 18, 19 for evaporating a refrigerant of a vapor compression type refrigerating cycle, a liquid storing unit 20 for storing the liquid phase refrigerant, a compressor 11 which sucks and compresses the refrigerant, and a flow passage forming member 110 to which a heat exchanger, the liquid storing unit, and the compressor are attached and which forms at least a part of flow passages of the refrigerant. The compressor is disposed below the flow passage forming member, and among the flow passages of the refrigerant, a suction refrigerant flow passage 28 through which the gas phase refrigerant to be sucked into the compressor flows has a rising portion 28a rising upward as going toward the compressor side.SELECTED DRAWING: Figure 5

Description

Technical Field

[0001] The present invention relates to a compressor module in which constituent devices of a vapor compression refrigeration cycle including a compressor are integrated.

Background Art

[0002] Conventionally, this type of compressor module has been disclosed in Patent Document 1. In the compressor module in this prior art, constituent devices such as a compressor, a condenser, an evaporator, a chiller, and an accumulator are placed on a base plate and connected to each other by refrigerant pipes.

Prior Art Documents

Patent Documents

[0003]

Patent Document 1

Summary of the Invention

Problems to be Solved by the Invention

[0004] In the above prior art, since a large number of refrigerant pipes exist in a narrow space, it is difficult to handle and connect the refrigerant pipes. As a countermeasure, the number of refrigerant pipes can be reduced by forming a refrigerant flow path inside the base plate.

[0005] However, since the refrigerant suction port of the compressor is often arranged at the upper part of the compressor, when a refrigerant flow path is formed inside the base plate, the refrigerant flow path between the base plate and the refrigerant suction port of the compressor becomes long, resulting in large heat loss and pressure loss. As a countermeasure, it is conceivable to arrange the compressor on the lower side of the base plate.

[0006] However, when the compressor is arranged on the lower side of the base plate, when the compressor stops, the liquid-phase refrigerant easily flows down from the base plate to the compressor due to gravity.

[0007] That is, when the compressor is in operation, the gaseous refrigerant existing inside the refrigerant flow path, heat exchanger, etc. radiates heat to the surroundings and condenses and liquefies over time as the compressor stops, and the liquefied refrigerant becomes more likely to flow down to the compressor by gravity.

[0008] If the compressor is restarted in a state where the liquid-phase refrigerant has accumulated in the compressor in this way, there is a risk that liquid compression will occur in the compressor, reducing the durability of the compressor.

[0009] In view of the above points, an object of the present invention is to suppress the occurrence of liquid compression when the compressor is restarted.

Means for Solving the Problems

[0010] To achieve the above object, the compressor module according to claim 1 includes: Evaporators (18, 19) for evaporating the refrigerant of the vapor compression refrigeration cycle; A liquid storage part (20) for storing the liquid-phase refrigerant; A compressor (11) for sucking and compressing the refrigerant; A flow path forming member (110) to which the evaporator, the liquid storage part, and the compressor are attached and which forms at least a part of the refrigerant flow path; The compressor is disposed on the lower side of the flow path forming member; Among the refrigerant flow paths, the suction refrigerant flow path (28) through which the gaseous refrigerant sucked into the compressor flows has a rising part (28a) that rises upward as it goes toward the compressor side.

[0011] According to this, even if the gaseous refrigerant radiates heat to the surroundings and condenses and liquefies when the compressor (11) stops, the rising part (28a) can suppress the liquefied refrigerant from flowing down to the compressor (11) by gravity. Therefore, it is possible to suppress the occurrence of liquid compression when the compressor (11) is restarted.

[0012] Note that the reference numerals in parentheses for each means described in this column and the claims indicate the correspondence with the specific means described in the embodiments described later.

Brief Description of the Drawings

[0013]

Figure 1

Figure 2

Figure 3

Figure 4

Figure 5

Figure 6

Figure 7

[0014] (First embodiment) The compressor module of this embodiment will be described with reference to Figs. 1 to 5. The compressor module of this embodiment is applied to a vehicle air conditioner 1 mounted on an electric vehicle. An electric vehicle is a vehicle that obtains driving force for traveling from an electric motor. The vehicle air conditioner 1 is a heat pump cycle device that performs air conditioning of the vehicle cabin, which is the space to be air-conditioned, and temperature adjustment of on-board equipment. Therefore, the vehicle air conditioner 1 can be called an air conditioner with an on-board equipment temperature adjustment function, or an on-board equipment temperature adjustment device with an air conditioning function.

[0015] Specifically, the vehicle air conditioner 1 adjusts the temperature of a battery (not shown) as an in-vehicle device. The battery is a secondary battery that stores power to be supplied to multiple in-vehicle devices that operate electrically. The battery is an assembled battery formed by electrically connecting multiple stacked battery cells in series or parallel. The battery cells in this embodiment are lithium-ion batteries.

[0016] The battery generates heat during operation (i.e., during charging and discharging). The battery has the characteristics that its output tends to decrease at low temperatures and its degradation tends to progress at high temperatures. Therefore, the temperature of the battery needs to be maintained within an appropriate temperature range (in this embodiment, 15°C or higher and 55°C or lower). Thus, in the electric vehicle of this embodiment, the vehicle air conditioner 1 is used to adjust the temperature of the battery.

[0017] The vehicle air conditioner 1 includes a heat pump cycle 10, a high-temperature heat medium circuit 30, a first low-temperature heat medium circuit 40, a second low-temperature heat medium circuit 50, an in-vehicle air conditioning unit (not shown), a control device (not shown), and the like.

[0018] The heat pump cycle 10 is a vapor compression refrigeration cycle device that adjusts the temperatures of the high-temperature heat medium circulating in the high-temperature heat medium circuit 30 and the low-temperature heat medium circulating in the first low-temperature heat medium circuit 40 and the second low-temperature heat medium circuit 50. The heat pump cycle 10 is configured to be able to switch the refrigerant circuit according to various operation modes for air conditioning in the vehicle interior and cooling of in-vehicle equipment.

[0019] The heat pump cycle 10 includes a compressor 11, a condenser 12, an intermediate-pressure expansion valve 13, a gas-liquid separator 14, an air-conditioning expansion valve 15, a cooling expansion valve 16, a hot gas flow adjustment valve 17, an air-conditioning chiller 18, a cooling chiller 19, an accumulator 20, an intermediate-pressure on-off valve 21, a bypass on-off valve 22, and the like.

[0020] In the heat pump cycle 10, an HFO-based refrigerant (specifically, R1234yf) is adopted as the refrigerant. The heat pump cycle 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. Refrigerant oil for lubricating the compressor 11 is mixed into the refrigerant. The refrigerant oil is PAG oil that is compatible with the liquid-phase refrigerant. A part of the refrigerant oil circulates in the cycle together with the refrigerant.

[0021] In the heat pump cycle 10, the compressor 11 sucks in refrigerant, compresses it, and discharges it. The compressor 11 is an electric compressor that drives a fixed displacement type compression mechanism with a fixed discharge capacity by an electric motor. The rotational speed (i.e., refrigerant discharge capacity) of the compressor 11 is controlled by a control signal output from the control device.

[0022] The compressor 11 is a two-stage boosting type electric compressor. The compressor 11, which is a two-stage boosting type electric compressor, houses two compression mechanisms, a low-stage side compression mechanism and a high-stage side compression mechanism, and an electric motor that rotationally drives both compression mechanisms inside the housing that forms its outer shell.

[0023] The housing of the compressor 11 is provided with a suction port 11a, an intermediate pressure port 11b, and a discharge port 11c. The suction port 11a is a suction port for sucking low-pressure refrigerant from outside the housing into the low-stage side compression mechanism. The discharge port 11c is a discharge port for discharging the high-pressure refrigerant discharged from the high-stage side compression mechanism to the outside of the housing.

[0024] The intermediate pressure port 11b is an intermediate pressure suction port for allowing intermediate pressure refrigerant to flow from outside the housing into the housing and merging it with the refrigerant in the compression process from low pressure to high pressure. That is, the intermediate pressure port 11b is connected to the discharge port side of the low-stage side compression mechanism and the suction port side of the high-stage side compression mechanism inside the housing.

[0025] Although the compressor 11 of the present embodiment houses two compression mechanisms in one housing, the form of the two-stage boosting type compressor is not limited to this. The compressor 11 of the present embodiment may be an electric compressor that houses one fixed displacement type compression mechanism and an electric motor that rotationally drives the compression mechanism inside the housing, as long as it is possible to allow intermediate pressure refrigerant to flow in from the intermediate pressure port 11b and merge it with the refrigerant in the compression process from low pressure to high pressure.

[0026] The compressor 11 of this embodiment may be an electric compressor that connects two compressors in series, uses the suction port of the low-stage compressor arranged on the low-stage side as the suction port 11a, uses the discharge port of the high-stage compressor arranged on the high-stage side as the discharge port 11c, and further provides an intermediate pressure port 11b at the connection part connecting the discharge port of the low-stage compressor and the suction port of the high-stage compressor, and constitutes a single two-stage boosting compressor by both the low-stage compressor and the high-stage compressor.

[0027] The condenser 12 is a heat exchange part that exchanges heat between the refrigerant discharged from the compressor 11 and the high-temperature heat medium in the high-temperature heat medium circuit 30. In the condenser 12, the heat of the refrigerant discharged from the compressor 11 is dissipated to the high-temperature heat medium, which is the fluid to be heated, to heat the high-temperature heat medium.

[0028] In the high-temperature heat medium circuit 30, a high-temperature heat medium pump, a heater core, a radiator, a switching valve, and an electric heater (none of which are shown in the figure) are arranged. The high-temperature heat medium pump sucks and discharges the high-temperature heat medium in the high-temperature heat medium circuit 30. The heater core is a heat exchanger that exchanges heat between the high-temperature heat medium in the high-temperature heat medium circuit 30 and the air blown into the vehicle interior to heat the air. The high-temperature heat medium in the high-temperature heat medium circuit 30 is, for example, an ethylene glycol aqueous solution.

[0029] The radiator is a heat exchanger that exchanges heat between the high-temperature heat medium in the high-temperature heat medium circuit 30 and the outside air to heat the air. The switching valve switches between a state where the high-temperature heat medium in the high-temperature heat medium circuit 30 flows through the heater core and a state where it flows through the radiator. The electric heater is a heat medium heater that generates heat when supplied with electric power to heat the high-temperature heat medium in the high-temperature heat medium circuit 30.

[0030] The intermediate pressure expansion valve 13 is a pressure reducing section that reduces the pressure of the refrigerant flowing out from the condenser 12 and adjusts the flow rate of the refrigerant flowing out to the downstream side. The operation of the intermediate pressure expansion valve 13 is controlled by a control signal (specifically, a control pulse) output from the control device. Therefore, the intermediate pressure expansion valve 13 is an electric device. The intermediate pressure expansion valve 13 has a fully open function in which it functions as a simple refrigerant flow path with almost no flow rate adjustment action and refrigerant pressure reduction action by fully opening the throttle passage.

[0031] The gas-liquid separator 14 has a refrigerant inlet 14a, a vapor-phase refrigerant outlet 14b, and a liquid-phase refrigerant outlet 14c. The refrigerant flowing out from the intermediate pressure expansion valve 13 flows into the refrigerant inlet 14a. The gas-liquid separator 14 separates the gas and liquid of the refrigerant flowing in from the refrigerant inlet 14a, allows the separated vapor-phase refrigerant to flow out from the vapor-phase refrigerant outlet 14b, and allows the separated liquid-phase refrigerant to flow out from the liquid-phase refrigerant outlet 14c.

[0032] The expansion valve 15 for cooling and the expansion valve 16 for cooling are pressure reducing sections that reduce the pressure of the liquid-phase refrigerant flowing out from the liquid-phase refrigerant outlet 14c of the gas-liquid separator 14 and adjust the flow rate of the refrigerant flowing out to the downstream side. The basic configuration of the expansion valve 15 for cooling and the expansion valve 16 for cooling is the same as that of the intermediate pressure expansion valve 13. Therefore, the expansion valve 15 for cooling and the expansion valve 16 for cooling are electric devices. The expansion valve 15 for cooling and the expansion valve 16 for cooling have a fully closed function in which they block the refrigerant flow path by fully closing the throttle passage.

[0033] The hot gas flow rate adjustment valve 17 is an electric variable throttle mechanism that reduces the pressure of the refrigerant flowing through the hot gas flow path 23 and adjusts the flow rate of the refrigerant flowing out to the downstream side. The basic configuration of the hot gas flow rate adjustment valve 17 is the same as that of the intermediate pressure expansion valve 13. Therefore, the hot gas flow rate adjustment valve 17 is an electric device. The hot gas flow rate adjustment valve 17 has a fully closed function in which it blocks the refrigerant flow path by fully closing the throttle passage.

[0034] The air-conditioning chiller 18 is a heat exchange section that exchanges heat between the low-pressure side refrigerant decompressed by the cooling expansion valve 15 and the low-temperature heat medium of the first low-temperature heat medium circuit 40. In the air-conditioning chiller 18, it is an evaporator that cools the low-temperature heat medium by evaporating the low-pressure side refrigerant to exert an endothermic effect.

[0035] In the first low-temperature heat medium circuit 40, a first low-temperature heat medium pump and a cooler core (both not shown) are arranged. The first low-temperature heat medium pump sucks and discharges the low-temperature heat medium of the first low-temperature heat medium circuit 40. The cooler core is a heat exchanger that exchanges heat between the low-temperature heat medium of the first low-temperature heat medium circuit 40 and the air blown into the vehicle interior to cool the air. The low-temperature heat medium of the first low-temperature heat medium circuit 40 is, for example, an ethylene glycol aqueous solution.

[0036] The cooling chiller 19 is a heat exchange section that exchanges heat between the low-pressure side refrigerant decompressed by the cooling expansion valve 16 and the low-temperature heat medium of the second low-temperature heat medium circuit 50. In the cooling chiller 19, it is an evaporator that cools the low-temperature heat medium by evaporating the low-pressure side refrigerant to exert an endothermic effect.

[0037] In the second low-temperature heat medium circuit 50, a second low-temperature heat medium pump and a battery (both not shown) are arranged. The second low-temperature heat medium pump sucks and discharges the low-temperature heat medium of the second low-temperature heat medium circuit 50. The cooler core is such that the low-temperature heat medium of the second low-temperature heat medium circuit 50 flows through the heat medium flow path in the battery, so that the low-temperature heat medium absorbs heat from the battery and the battery is cooled. The low-temperature heat medium of the second low-temperature heat medium circuit 50 is, for example, an ethylene glycol aqueous solution.

[0038] The accumulator 20 is a low-pressure side gas-liquid separator that separates the gas and liquid of the refrigerant flowing into it and stores the surplus liquid-phase refrigerant in the cycle. The accumulator 20 is a liquid storage section.

[0039] The intermediate pressure on-off valve 21 is a solenoid valve that opens and closes the intermediate pressure flow path 24. The intermediate pressure on-off valve 21 is a solenoid valve whose opening and closing operation is controlled by a control voltage output from a control device. Therefore, the intermediate pressure on-off valve 21 is an electric device. The intermediate pressure flow path 24 is connected to the gas-phase refrigerant outlet 14b of the gas-liquid separator 14 and the intermediate pressure port 11b of the compressor 11.

[0040] The bypass on-off valve 22 is a solenoid valve that opens and closes the bypass flow path 25. The bypass on-off valve 22 is a solenoid valve whose opening and closing operation is controlled by a control voltage output from a control device. Therefore, the bypass on-off valve 22 is an electric device.

[0041] The heat pump cycle 10 has a first branch portion 26a, a second branch portion 26b, and a third branch portion 26c that branch the flow of the refrigerant. The heat pump cycle 10 has a first confluence portion 27a, a second confluence portion 27b, and a third confluence portion 27c that merge the flow of the refrigerant.

[0042] The first branch portion 26a branches the flow of the refrigerant discharged from the compressor 11 into the condenser 12 side and the hot gas flow path 23 side. The second branch portion 26b branches the flow of the liquid-phase refrigerant flowing out from the liquid-phase refrigerant outlet 14c of the gas-liquid separator 14 into the cooling expansion valve 15 side and the cooling expansion valve 16 side. The third branch portion 26c branches the flow of the refrigerant merged at the first confluence portion 27a into the accumulator 20 side and the bypass flow path 25 side.

[0043] The first confluence portion 27a merges the flow of the refrigerant flowing out from the hot gas flow path 23 and the flow of the refrigerant evaporated in the air-conditioning chiller 18. The second confluence portion 27b merges the flow of the refrigerant flowing out from the bypass flow path 25 and the flow of the gas-phase refrigerant flowing out from the accumulator 20. The third confluence portion 27c merges the flow of the refrigerant evaporated in the cooling chiller 19 and the flow of the refrigerant merged at the second confluence portion 27b.

[0044] An intake refrigerant flow path 28 is connected between the refrigerant outlet of the third confluence portion 27c and the intake port 11a of the compressor 11.

[0045] The in-vehicle air conditioning unit (not shown) is a unit that integrates a plurality of component devices in order to blow out air adjusted to an appropriate temperature for air conditioning in the vehicle interior to appropriate locations in the vehicle interior. The in-vehicle air conditioning unit is disposed inside the instrument panel at the foremost part of the vehicle interior.

[0046] The in-vehicle air conditioning unit is formed by accommodating an in-vehicle blower (not shown), a cooler core, a heater core, etc. in an air conditioning case (not shown) that forms an air passage.

[0047] The heat pump cycle 10 has a refrigerant pressure sensor group and a refrigerant temperature sensor group. The refrigerant pressure sensor group includes an intake refrigerant pressure sensor 61, a discharge refrigerant pressure sensor 62, etc. The intake refrigerant pressure sensor 61 is a refrigerant pressure sensor that detects the pressure of the refrigerant sucked into the intake port 11a of the compressor 11. The discharge refrigerant pressure sensor 62 is a refrigerant pressure sensor that detects the pressure of the refrigerant discharged from the discharge port 11c of the compressor 11.

[0048] The refrigerant temperature sensor group includes a condensed refrigerant temperature sensor 63, an evaporated refrigerant temperature sensor 64, etc. The condensed refrigerant temperature sensor 63 is a refrigerant temperature sensor that detects the temperature of the refrigerant flowing out of the condenser 12. The evaporated refrigerant temperature sensor 64 is a refrigerant temperature sensor that detects the temperature of the refrigerant flowing out of the cooling chiller 19.

[0049] The detection signals of the refrigerant pressure sensor group and the refrigerant temperature sensor group are input to the control device. The control device has a well-known microcomputer including a CPU, a ROM, a RAM, etc. and its peripheral circuits. The control device performs various calculations and processes based on the control program stored in the ROM. Then, the control device controls the operation of various controlled devices connected to the output side based on the calculation and processing results.

[0050] An operation panel (not shown) is connected to the input side of the control device. The operation panel is arranged near the instrument panel at the front part of the vehicle interior and is provided with various operation switches. Operation signals from the various operation switches provided on the operation panel are input to the control device.

[0051] Specific examples of the various operation switches provided on the operation panel include an auto switch, an air conditioner switch, an air volume setting switch, a temperature setting switch, etc.

[0052] The auto switch is an operation switch for setting or canceling the automatic control operation of the vehicle air conditioner 1. The air conditioner switch is an operation switch for requesting cooling of air by the cooler core. The air volume setting switch is an operation switch for manually setting the air volume of the air blown into the vehicle interior (i.e., the air volume of the interior blower). The temperature setting switch is an operation switch for setting the set temperature of the vehicle interior.

[0053] The compressor module 100 shown in FIGS. 2 and 3 is a component that integrates a plurality of component devices mainly constituting the heat pump cycle 10. The vertical arrows in FIGS. 2 and 3 indicate the vertical direction of the electric vehicle on which the compressor module 100 is mounted.

[0054] In the compressor module 100 of the present embodiment, among the component devices of the heat pump cycle 10, the compressor 11, the condenser 12, the intermediate pressure expansion valve 13, the gas-liquid separator 14, the refrigeration expansion valve 15, the cooling expansion valve 16, the hot gas flow control valve 17, the air conditioning chiller 18, the cooling chiller 19, the accumulator 20, the intermediate pressure on-off valve 21, the bypass on-off valve 22, etc. are integrated.

[0055] These component devices are integrated by being attached to the flow path plate 110 of the compressor module 100. Therefore, the flow path plate 110 is a mounting member for attaching a plurality of component devices.

[0056] The flow path plate 110 is formed by casting with a metal (in this embodiment, an aluminum alloy). The flow path plate 110 is formed in a plate shape extending in the horizontal direction.

[0057] On the upper surface of the flow path plate 110, a condenser 12, an intermediate pressure expansion valve 13, a gas-liquid separator 14, a refrigeration expansion valve 15, a cooling expansion valve 16, a hot gas flow control valve 17, an air-conditioning chiller 18, a cooling chiller 19, and a bypass on-off valve 22 are fixed. The intermediate pressure on-off valve 21 is integrated with the gas-liquid separator 14.

[0058] On the lower surface of the flow path plate 110, a compressor 11 and an accumulator 20 are fixed. A bracket (not shown) is attached to the side surface of the flow path plate 110. The bracket is a member used to fix the compressor module 100 to the vehicle. For example, the bracket extends downward so as to straddle the compressor 11 and the accumulator 20.

[0059] Inside the flow path plate 110 is a flow path forming member in which a plurality of refrigerant flow paths for circulating the refrigerant of the heat pump cycle 10, a plurality of heat medium flow paths for circulating the high-temperature heat medium of the high-temperature heat medium circuit 30, and a plurality of heat medium flow paths for circulating the low-temperature heat medium of the first low-temperature heat medium circuit 40 and the second low-temperature heat medium circuit 50 are formed.

[0060] The first branch portion 26a, the second branch portion 26b, the third branch portion 26c, the first confluence portion 27a, the second confluence portion 27b, and the third confluence portion 27c are formed inside the flow path plate 110.

[0061] As shown in FIG. 4, on the upper surface of the flow path plate 110, a plurality of seat portions 111a for fixing the condenser 12, a plurality of seat portions 111b for fixing the air-conditioning chiller 18, and a plurality of seat portions 111c for fixing the cooling chiller 19 are formed. The vertical arrow in FIG. 4 indicates the vertical direction of the electric vehicle on which the compressor module 100 is mounted.

[0062] On the upper surface of the flow path plate 110, there are formed an outlet 112a of the refrigerant to the condenser 12, an inlet 112b of the refrigerant from the condenser 12, an outlet 112c of the refrigerant to the air-conditioning chiller 18, an inlet 112d of the refrigerant from the air-conditioning chiller 18, an outlet 112e of the refrigerant to the cooling chiller 19, and an inlet 112f of the refrigerant from the cooling chiller 19.

[0063] On the upper surface of the flow path plate 110, there are formed an outlet 113a of the high-temperature heat medium to the condenser 12, an outlet 113c of the low-temperature heat medium to the air-conditioning chiller 18, an inlet 113d of the low-temperature heat medium from the air-conditioning chiller 18, an outlet 113e of the low-temperature heat medium to the cooling chiller 19, and an inlet 113f of the low-temperature heat medium from the cooling chiller 19.

[0064] On the upper surface of the flow path plate 110, there are formed mounting holes 114a to which the intermediate-pressure expansion valve 13 is attached, mounting holes 114b to which the gas-liquid separator 14 is attached, mounting holes 114c to which the cooling expansion valve 15 is attached, mounting holes 114d to which the cooling expansion valve 16 is attached, mounting holes 114e to which the hot gas flow control valve 17 is attached, and mounting holes 114f to which the bypass on-off valve 22 is attached.

[0065] On the upper surface of the flow path plate 110, there are formed a high-temperature heat medium inlet 115a through which the high-temperature heat medium flows in, a low-temperature heat medium inlet 115b through which the low-temperature heat medium flows in, and a high-temperature heat medium outlet 115c through which the low-temperature heat medium flows out.

[0066] On the upper surface of the flow path plate 110, there is formed a suction refrigerant outlet 116. The suction refrigerant outlet 116 is the refrigerant outlet of the third confluence portion 27c. As shown in FIGS. 2, 3, and 5, outside the flow path plate 110, a discharge refrigerant pipe 120, an intermediate-pressure refrigerant pipe 121, and a suction refrigerant pipe 122 are arranged. The vertical arrows in FIGS. 2, 3, and 5 indicate the vertical direction of the electric vehicle on which the compressor module 100 is mounted.

[0067] The discharge refrigerant pipe 120 is a flow path forming member that forms a refrigerant flow path 29 between the discharge port 11c of the compressor 11 shown in FIG. 1 and the first branch portion 26a.

[0068] The intermediate-pressure refrigerant pipe 121 is a flow path forming member that forms a flow path between the intermediate-pressure on-off valve 21 and the intermediate-pressure port 11b of the compressor 11 in the intermediate-pressure flow path 24 shown in FIG. 1. The suction refrigerant pipe 122 is a flow path forming member that forms a suction refrigerant flow path 28.

[0069] As schematically shown in FIG. 5, after the suction refrigerant pipe 122 rises upward from the suction refrigerant outlet 116 that opens on the upper surface of the flow path plate 110, it hangs downward toward the through hole 117 of the flow path plate 110, and further passes through the through hole 117 of the flow path plate 110 and hangs downward to below the flow path plate 110 and is connected to the suction port 11a of the compressor 11.

[0070] The portion of the suction refrigerant pipe 122 that rises upward from the suction refrigerant outlet 116 of the third confluence portion 27c forms a rising portion 28a that raises the suction refrigerant flow path 28 upward in the gravitational direction.

[0071] Next, the operation of the vehicle air conditioner 1 of the present embodiment in the above configuration will be described. In the vehicle air conditioner 1 of the present embodiment, various operation modes are switched in order to perform air conditioning in the vehicle interior and temperature adjustment of the battery. The switching of the operation mode is performed by executing a control program stored in advance in the control device. The operation mode is switched by the control device controlling the operations of the intermediate-pressure expansion valve 13, the cooling expansion valve 15, the cooling expansion valve 16, the hot gas flow rate adjustment valve 17, the intermediate-pressure on-off valve 21, and the bypass on-off valve 22.

[0072] Examples of the various operation modes of the vehicle air conditioner 1 include a single cooling mode, a cooling and cooling mode, a single dehumidifying and heating mode, a cooling dehumidifying and heating mode, a single cooling mode, and the like.

[0073] The single cooling mode is an operation mode in which the interior of the vehicle is cooled by blowing out the air cooled by the cooler core into the vehicle interior.

[0074] The cooling and cooling mode is an operation mode in which the interior of the vehicle is cooled by blowing out the air cooled by the cooler core into the vehicle interior, and the battery is cooled by the low-temperature heat medium cooled by the cooling chiller 19.

[0075] The single dehumidifying and heating mode is an operation mode in which the interior of the vehicle is dehumidified and heated by heating the air cooled by the cooler core with the heater core and blowing it into the vehicle interior.

[0076] The cooling dehumidifying and heating mode is an operation mode in which the interior of the vehicle is dehumidified and heated by heating the air cooled by the cooler core with the heater core and blowing it into the vehicle interior, and the battery is cooled by the low-temperature heat medium cooled by the cooling chiller 19.

[0077] The single cooling mode is an operation mode in which the battery is cooled by the low-temperature heat medium cooled by the cooling chiller 19.

[0078] By setting the hot gas flow control valve 17 to a throttled state, the refrigerant with a low enthalpy flowing out from at least one of the air-conditioning chiller 18 and the cooling chiller 19 is mixed with the refrigerant with a high enthalpy flowing out from the hot gas flow path 23 and is sucked into the compressor 11.

[0079] The control device controls the throttle opening degree of the hot gas flow control valve 17 so that the superheat degree of the refrigerant sucked into the compressor 11 approaches the target superheat degree, whereby the state of the refrigerant sucked into the compressor 11 can be a vapor-phase refrigerant having a superheat degree.

[0080] By setting the intermediate pressure opening / closing valve 21 to the open state, the gaseous intermediate pressure refrigerant that has passed through the intermediate pressure expansion valve 13 and the gas-liquid separator 14 can flow into the intermediate pressure port 11b of the compressor 11. Therefore, the gaseous intermediate pressure refrigerant that has passed through the intermediate pressure expansion valve 13 and the gas-liquid separator 14 can be merged with the refrigerant in the pressure boosting process that is inhaled from the suction port 11a in the compressor 11. That is, the heat pump cycle 10 can constitute a gas injection cycle.

[0081] By setting the bypass opening / closing valve 22 to the open state, a part of the refrigerant that has merged at the first merging portion 27a can bypass the accumulator 20 and flow into the bypass flow path 25. Thereby, the pressure loss of the refrigerant in the accumulator 20 can be reduced and the performance of the heat pump cycle 10 can be improved.

[0082] In these operation modes, in the refrigerant flow path of the heat pump cycle 10, there are a region where the liquid-phase refrigerant flows and a region where the gaseous-phase refrigerant flows. The gaseous-phase refrigerant decompressed by the hot gas flow rate adjustment valve 17, the gaseous-phase refrigerant evaporated in the air-conditioning chiller 18, and the gaseous-phase refrigerant evaporated in the cooling chiller 19 are inhaled into the suction port 11a of the compressor 11 through the suction refrigerant flow path 28 in the suction refrigerant pipe 122 from the third merging portion 27c.

[0083] When the heat pump cycle 10 stops operating (in other words, when the compressor 11 stops), the high-temperature gaseous-phase refrigerant in the refrigerant flow path, the gaseous-phase refrigerant in the air-conditioning chiller 18, and the gaseous-phase refrigerant in the cooling chiller 19 dissipate heat to the surroundings over time and condense and liquefy.

[0084] During the operation stop of the heat pump cycle 10, the refrigerant condensed and liquefied flows downward from the higher position to the lower position in the refrigerant flow path of the heat pump cycle 10 due to the action of gravity. When the refrigerant condensed and liquefied during the operation stop of the heat pump cycle 10 flows down and flows into the suction port 11a of the compressor 11 from the flow path plate 110, when the heat pump cycle 10 is restarted (in other words, when the compressor is restarted), there is a risk that the liquid-phase refrigerant accumulated in the compressor 11 will be compressed and the durability of the compressor 11 will be reduced.

[0085] In this regard, in the present embodiment, since the suction refrigerant pipe 122 rises upward from the suction refrigerant outlet 116 of the flow path plate 110, it is possible to suppress the refrigerant condensed and liquefied during the operation stop of the heat pump cycle 10 from flowing down to the suction port 11a of the compressor 11 due to gravity. Therefore, it is possible to suppress the occurrence of liquid compression in the compressor 11 when the compressor is restarted.

[0086] In the present embodiment, the compressor 11 is disposed on the lower side of the flow path plate 110, and the suction refrigerant flow path 28 has a rising portion 28a that rises upward as it goes toward the compressor 11 side.

[0087] According to this, even when the gaseous refrigerant radiates heat to the surroundings and condenses and liquefies when the compressor 11 stops, it is possible to suppress the liquefied refrigerant from flowing down from the flow path plate 110 to the compressor 11 due to gravity by the rising portion 28a. Therefore, it is possible to suppress the occurrence of liquid compression when the compressor 11 is restarted.

[0088] In the present embodiment, the accumulator 20 is disposed on the lower side of the flow path plate 110. According to this, when the compressor 11 stops, the liquefied refrigerant easily flows down to the accumulator 20 due to gravity and accumulates in the accumulator 20. Therefore, it is possible to suppress the liquefied refrigerant from flowing down from the flow path plate 110 to the compressor 11 due to gravity, so it is possible to suppress the occurrence of liquid compression when the compressor 11 is restarted.

[0089] In this embodiment, the air-conditioning chiller 18 and the cooling chiller 19 are arranged above the flow path plate 110. As a result, the air-conditioning chiller 18 and the cooling chiller 19 and the compressor 11 can be efficiently arranged separately on the upper and lower sides of the flow path plate 110.

[0090] In this embodiment, since the suction refrigerant pipe 122 rises upward from the suction refrigerant outlet 116 of the flow path plate 110, a rising portion 28a is formed. As a result, the rising portion 28a can be easily formed.

[0091] In this embodiment, the flow path plate 110 is a plate-like member that extends in the horizontal direction, and the compressor 11 is fixed to the lower surface of the flow path plate 110. As a result, the compressor 11 and other component devices of the heat pump cycle 10 can be efficiently arranged on the flow path plate 110.

[0092] (Second Embodiment) In the first embodiment, the suction refrigerant flow path 28 is formed by the suction refrigerant pipe 122. However, in this embodiment, as shown in FIG. 6, the suction refrigerant flow path 28 is formed inside the flow path plate 110, and a rising portion 28a of the suction refrigerant flow path 28 is formed inside the flow path plate 110. The vertical arrow in FIG. 6 indicates the vertical direction of the electric vehicle on which the compressor module 100 is mounted.

[0093] In this embodiment, the suction refrigerant outlet 116 is formed on the lower surface of the flow path plate 110 and is directly connected to the suction port 11a of the compressor 11.

[0094] Similar to the first embodiment, the rising portion 28a of the suction refrigerant flow path 28 can suppress the condensed and liquefied refrigerant from flowing down to the compressor 11 during the stop of operation, so that liquid compression can be suppressed during the restart of the compressor 11.

[0095] In the present embodiment, since the rising portion 28a is formed inside the flow path plate 110, the rising portion 28a can be formed while suppressing an increase in the size of the compressor module 100 as much as possible.

[0096] (Third Embodiment) In the present embodiment, as shown in FIG. 7, a liquid reservoir portion 119 recessed downward is formed in the refrigerant flow path 118 inside the flow path plate 110. The vertical arrow in FIG. 7 indicates the vertical direction of the electric vehicle on which the compressor module 100 is mounted.

[0097] During operation stop, the refrigerant condensed and liquefied accumulates in the liquid reservoir portion 119. Therefore, it is possible to suppress the refrigerant condensed and liquefied during operation stop from flowing into the compressor 11 when the compressor 11 restarts.

[0098] In the above embodiment, the accumulator 20 is disposed below the flow path plate 110 so that the refrigerant condensed during operation stop is likely to accumulate in the accumulator 20. This is because the refrigerant condensed and liquefied during operation stop easily flows down from the flow path plate 110 to the accumulator 20 by gravity.

[0099] In the present embodiment, since the liquid reservoir portion 119 is formed, a liquid-phase refrigerant can be stored inside the flow path plate 110, so that the accumulator 20 can be disposed laterally or above the flow path plate 110.

[0100] In the above embodiment, the air-conditioning chiller 18 is disposed above the flow path plate 110 so that the refrigerant condensed and liquefied by the air-conditioning chiller 18 during operation stop is likely to accumulate in the accumulator 20, and the accumulator 20 is disposed below the flow path plate 110. This is because the refrigerant condensed and liquefied by the air-conditioning chiller 18 during operation stop easily flows down to the accumulator 20 by gravity. Thereby, it is possible to suppress the refrigerant condensed and liquefied by the air-conditioning chiller 18 during operation stop from flowing into the compressor 11 through the bypass flow path 25 when the compressor 11 restarts.

[0101] On the other hand, if the liquid reservoir portion 119 of the present embodiment is formed in the bypass passage 25, it is possible to suppress the refrigerant condensed and liquefied by the air-conditioning chiller 18 during operation stop from flowing into the compressor 11 through the bypass passage 25 when the compressor 11 restarts. Therefore, it becomes possible to dispose the air-conditioning chiller 18 below the flow path plate 110.

[0102] When the suction refrigerant passage 28 is formed inside the flow path plate 110 as in the second embodiment, a liquid reservoir portion 119 may be formed in the suction refrigerant passage 28.

[0103] In the present embodiment, the flow path plate 110 has a liquid reservoir portion 119 in which the refrigerant flow path 118 is recessed downward so that the liquid-phase refrigerant accumulates.

[0104] According to this, since the refrigerant liquefied when the compressor 11 stops accumulates in the liquid reservoir portion 119, it is possible to suppress the liquefied refrigerant from flowing down to the compressor 11 by gravity. Therefore, it is possible to suppress the occurrence of liquid compression when the compressor 11 restarts.

[0105] (Other embodiments) The present invention is not limited to the above-described embodiments, and can be variously modified as follows, for example.

[0106] (1) In the above-described embodiment, the vehicle air conditioner 1 has been described as the heat pump cycle apparatus to which the compressor module is applied, but the heat pump cycle apparatus to which the compressor module is applied is not limited to the vehicle air conditioner.

[0107] For example, it may be a stationary air conditioner with a temperature adjustment function that adjusts the temperature of a temperature adjustment object (for example, a computer, a computer server device, or other electric devices) while performing indoor air conditioning.

[0108] In the above-described embodiment, an example in which the temperature of the battery is adjusted has been described as the in-vehicle device whose temperature is to be adjusted. However, the in-vehicle device is not limited to the battery. For example, the temperature of an inverter, a PCU, a transaxle, a control device for ADAS, or the like may be adjusted.

[0109] The inverter supplies power to a motor generator or the like. The PCU is a power control unit that performs power conversion and power distribution. The transaxle is a power transmission mechanism that integrates a transmission, a differential gear, and the like. The control device for ADAS is a control device for an advanced driver assistance system.

[0110] (2) The specific configuration of the compressor module 100 is not limited to the configuration disclosed in the above-described embodiment.

[0111] For example, each component device of the heat pump cycle 10 integrated into the compressor module 100 is not limited to the component device disclosed in the above-described embodiment. As long as at least the compressor 11, at least one evaporator, and the accumulator 20 are integrated into the flow path plate 110, the other component devices may or may not be integrated.

[0112] In the above-described embodiment, an example in which an aluminum alloy is adopted as the material for forming the flow path plate 110 has been described. However, the material of the flow path plate 110 is not limited to the aluminum alloy.

[0113] (3) The specific configuration of the heat pump cycle device to which the compressor module is applied is not limited to the configuration disclosed in the above-described embodiment.

[0114] For example, the refrigerant of the heat pump cycle 10 is not limited to R1234yf. As the refrigerant, R134a, R600a, R410A, R404A, R32, R407C, or the like may be adopted. Alternatively, a mixed refrigerant in which a plurality of these refrigerants are mixed may be adopted.

[0115] For example, the high-temperature heat medium in the high-temperature heat medium circuit 30, and the low-temperature heat media in the first low-temperature heat medium circuit 40 and the second low-temperature heat medium circuit 50 are not limited to an ethylene glycol aqueous solution. As the high-temperature heat medium and the low-temperature heat media, dimethylpolysiloxane, or a solution containing a nanofluid or the like, an antifreeze, an aqueous liquid refrigerant containing alcohol or the like, or a liquid medium containing oil or the like may be employed.

[0116] (4) The operating mode of the heat pump cycle 10 to which the compressor module is applied is not limited to the mode disclosed in the above-described embodiment.

[0117] (5) The refrigerant flow path inside the flow path plate 110 may be provided with an inclination or a step so that the refrigerant flow path inside the flow path plate 110 descends downward toward the accumulator 20.

[0118] In the above-described embodiment, since the refrigerant condensed during the operation stop naturally flows down by gravity and easily accumulates in the accumulator 20, the inflow into the compressor 11 at the time of restart can be suppressed.

[0119] (6) In the above-described embodiment, the flow path plate 110 is formed by casting, but the flow path plate 110 may be formed by bonding metal plates or combining cutting blocks.

[0120] The features of the compressor module disclosed in this specification are shown as follows.

[0121] (Item 1) Evaporators (18, 19) for evaporating the refrigerant of the vapor compression refrigeration cycle, A liquid storage section (20) for storing the liquid-phase refrigerant, A compressor (11) for sucking and compressing the refrigerant, Comprising an evaporator, the liquid storage section, the compressor being attached, and a flow path forming member (110) forming at least a part of the flow path of the refrigerant, The compressor is disposed on the lower side of the flow path forming member, Of the refrigerant flow paths, the suction refrigerant flow path (28) through which the gaseous refrigerant sucked into the compressor flows has a rising portion (28a) that rises upward as it goes toward the compressor side. A compressor module.

[0122] (Item 2) The compressor module according to item 1, wherein the liquid storage portion is disposed below the flow path forming member.

[0123] (Item 3) The compressor module according to item 1 or 2, wherein the evaporator is disposed above the flow path forming member.

[0124] (Item 4) Comprises a suction refrigerant pipe (122) which is a pipe member forming a passage of the refrigerant from the flow path forming member to the compressor in the suction refrigerant flow path, In the flow path forming member, a suction refrigerant outlet (116) through which the refrigerant flows out and to which the suction refrigerant pipe is connected is formed, The compressor module according to any one of items 1 to 3, wherein the rising portion (28a) is formed by the suction refrigerant pipe rising upward from the suction refrigerant outlet.

[0125] (Item 5) The flow path forming member is a plate-like member that extends in the horizontal direction, The compressor module according to any one of items 1 to 4, wherein the compressor is fixed to the lower surface of the flow path forming member.

[0126] (Item 6) The compressor module according to any one of items 1 to 5, wherein the flow path forming member has a liquid reservoir portion (119) that depresses the refrigerant flow path downward so that the liquid-phase refrigerant accumulates.

[0127] (Item 7) The compressor module according to any one of items 1 to 6, wherein the rising portion is formed inside the flow path forming member.

Description of Symbols

[0128] 11 Compressor 18 Chiller for air conditioning (evaporator) 19 Chiller for cooling (evaporator) 20 Accumulator (liquid storage section) 28 Suction refrigerant flow path 28a Rising section 110 Flow path plate (flow path forming member) 116 Suction refrigerant outlet 122 Suction refrigerant pipe

Claims

1. An evaporator (18, 19) for evaporating the refrigerant in a vapor compression refrigeration cycle, A liquid storage section (20) for storing the liquid-phase refrigerant, A compressor (11) for sucking and compressing the refrigerant, An evaporator, the liquid storage section, and the compressor are attached, and a flow path forming member (110) that forms at least a part of the flow path of the refrigerant is provided, The compressor is disposed on the lower side of the flow path forming member, Among the flow paths of the refrigerant, an intake refrigerant flow path (28) through which the gaseous refrigerant sucked into the compressor flows has a rising portion (28a) that rises upward as it goes toward the compressor side. A compressor module.

2. The compressor module according to claim 1, wherein the liquid storage section is disposed on the lower side of the flow path forming member.

3. The compressor module according to claim 1 or 2, wherein the evaporator is disposed on the upper side of the flow path forming member.

4. An intake refrigerant pipe (122) that is a piping member forming a passage of the refrigerant from the flow path forming member to the compressor among the intake refrigerant flow paths, An intake refrigerant outlet (116) through which the refrigerant flows out and to which the intake refrigerant pipe is connected is formed in the flow path forming member, The compressor module according to claim 1 or 2, wherein the rising portion (28a) is formed by the intake refrigerant pipe rising upward from the intake refrigerant outlet.

5. The flow path forming member is a plate-like member that expands in the horizontal direction, The compressor module according to claim 1 or 2, wherein the compressor is fixed to the lower surface of the flow path forming member.

6. The compressor module according to claim 1 or 2, wherein the flow path forming member has a liquid reservoir portion (119) in which the flow path of the refrigerant is recessed downward so that the liquid-phase refrigerant accumulates.

7. The compressor module according to claim 1 or 2, wherein the rising portion is formed inside the flow path forming member.

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