Compressor Module

Abstract

To provide a compressor module which can sufficiently suppress noise without deteriorating productivity of a heat pump cycle device.SOLUTION: A compressor module 100 includes: a passage box 101 formed with an internal refrigerant passage; and a cover member 102 which forms a housing space 103 which houses a compressor 11 with the passage box 101. A housing space 103 side inner surface of the passage box 101 is formed with: a compressor side inlet 101b connected with the discharge port side of the compressor 11; and a compressor side outlet 101a connected with the suction port side of the compressor 11. An outer surface of the passage box 101 is formed with outer connection ports, such as a condenser side outlet 121c and a condenser side inlet 121d, with which an inflow outlet of an external component, such as an indoor condenser 14, is connected.SELECTED DRAWING: Figure 2

Description

[Technical field]

[0001] The present invention relates to a compressor module in which components of a heat pump cycle device, including a compressor, are integrated. [Background technology]

[0002] Conventionally, Patent Document 1 discloses a compressor module in which components of a heat pump cycle device, such as a compressor and a manifold, are integrated. The manifold is a passage forming member or a passage connecting member in which refrigerant piping and heat medium piping are formed. This type of compressor module is effective for improving the productivity of the heat pump cycle device. Furthermore, Patent Document 1 attempts to suppress the noise of the compressor module by covering the integrated compressor, manifold, etc. with a cover member for noise suppression. [Prior art documents] [Patent documents]

[0003] [Patent Document 1] US Patent Application Publication No. 2019 / 0039440 Summary of the Invention [Problem to be solved by the invention]

[0004] However, as in Patent Document 1, simply covering the compressor, manifold, and the like with a cover member cannot sufficiently suppress the noise of the compressor module. The reason is that in order to take the refrigerant piping and heat medium piping connected to the manifold out of the cover member, through holes penetrating the inside and outside of the cover member must be formed. As a result, the noise of the compressor leaks out of the cover member through the gap between the through holes and the piping.

[0005] In order to sufficiently suppress the noise of the compressor module, a method of sealing the gap between the through hole and the pipe with a soundproof sealing member is considered. However, sealing the gap between the through hole and the pipe with a sealing member causes a decrease in productivity of the heat pump cycle device.

[0006] In view of the above, an object of the present invention is to provide a compressor module that can sufficiently suppress noise without causing a decrease in productivity of a heat pump cycle device. [Means for solving the problem]

[0007] In order to achieve the above object, a compressor module according to claim 1 is applied to a heat pump cycle apparatus (1, 1a, 1b), and includes a compressor (11), a passage forming member (101, 111, 121, 131), and a cover member (102, 122, 132).

[0008] The compressor draws in a refrigerant, compresses it, and discharges it. The passage forming member has a plurality of internal refrigerant passages formed therein through which the refrigerant flows. The cover member, together with the passage forming member, forms an accommodation space (103, 113, 123) that accommodates the compressor.

[0009] The storage space has compressor side inlets (101b, 111b, 121b, 131b) and compressor side outlets (101a, 111a, 121a, 131a) formed therein and communicating with the internal refrigerant passage. The storage space has outer connection ports (101c-101h, 111g, 111h, 121c-121h, 131c-131h) formed thereoutside and communicating with the internal refrigerant passage.

[0010] The compressor side inlet is connected to the discharge port side of the compressor. The outer connection port is connected to the inlet / outlet sides of the external component devices (14, 16, 18) that are disposed outside the accommodation space, among the component devices of the heat pump cycle apparatus. Furthermore, at least a portion of the outer surface is formed by both the passage forming member and the cover member.

[0011] This allows the refrigerant discharged from the compressor (11) to flow through the internal refrigerant passage to the external components (14, 16, 18). Similarly, the refrigerant flowing out from the external components (14, 16, 18) can be sucked into the compressor (11) through the internal refrigerant passage.

[0012] Therefore, there is no need to form through holes or the like in the passage forming members (101...131) or the cover members (102...132) for passing piping connecting the compressor (11) and the external components (14, 16, 18). This prevents noise from the compressor (11) from leaking out of the accommodation space (103...133) through gaps between the through holes and the piping. Furthermore, there is no need to seal the gaps between the through holes and the piping with soundproof sealing members or the like.

[0013] As a result, according to the invention recited in claim 1, it is possible to provide a compressor module capable of sufficiently suppressing noise without causing a decrease in productivity of the heat pump cycle apparatus (1, 1a, 1b). A compressor module according to a second aspect of the present invention is applied to a heat pump cycle apparatus (1, 1a, 1b), and includes a compressor (11), a passage forming member (101, 111, 121, 131), and a cover member (102, 122, 132). The compressor draws in a refrigerant, compresses it, and discharges it. The passage forming member has a plurality of internal refrigerant passages formed therein through which the refrigerant flows. The cover member, together with the passage forming member, forms an accommodation space (103, 113, 123) that accommodates the compressor. The storage space has compressor side inlets (101b, 111b, 121b, 131b) and compressor side outlets (101a, 111a, 121a, 131a) formed therein and communicating with the internal refrigerant passage. The storage space has outer connection ports (101c-101h, 111g, 111h, 121c-121h, 131c-131h) formed thereoutside and communicating with the internal refrigerant passage. The compressor side inlet is connected to the discharge port side of the compressor. The outer connection port is connected to the inlet / outlet sides of the external component devices (14, 16, 18) that are disposed outside the accommodation space, among the component devices of the heat pump cycle apparatus. The compressor is fixed to the passage forming member via a vibration isolating member (11c). The passage forming member has a portion forming a high-pressure side refrigerant device (12, 141, 24) into which the high-pressure side refrigerant of the heat pump cycle device flows, among the components of the heat pump cycle device, and the vibration isolating member has thermoplasticity and is arranged so as to be heatable by the high-pressure side refrigerant in the high-pressure side refrigerant device. According to this, the same effect as that of the compressor module according to claim 1 can be obtained. A compressor module according to a fourth aspect of the present invention is applied to a heat pump cycle apparatus (1, 1a, 1b), and includes a compressor (11), a passage forming member (101, 111, 121, 131), and a cover member (102, 122, 132). The compressor draws in a refrigerant, compresses it, and discharges it. The passage forming member has a plurality of internal refrigerant passages formed therein through which the refrigerant flows. The cover member, together with the passage forming member, forms an accommodation space (103, 113, 123) that accommodates the compressor. The storage space has compressor side inlets (101b, 111b, 121b, 131b) and compressor side outlets (101a, 111a, 121a, 131a) formed therein and communicating with the internal refrigerant passage. The storage space has outer connection ports (101c-101h, 111g, 111h, 121c-121h, 131c-131h) formed thereoutside and communicating with the internal refrigerant passage. The compressor side inlet is connected to the discharge port side of the compressor. The outer connection port is connected to the inlet / outlet sides of the external component devices (14, 16, 18) that are disposed outside the accommodation space, among the component devices of the heat pump cycle apparatus. The compressor is fixed to the passage forming member via a vibration isolating member (11c). The vibration isolating member has thermoplastic properties and is arranged so as to be heatable by heat generated by the compressor. According to this, the same effect as that of the compressor module according to claim 1 can be obtained.

[0014] The reference symbols in parentheses for each means described in this section and in the claims are examples showing the correspondence with the specific means described in the embodiments described later. [Brief description of the drawings]

[0015] [Figure 1] 1 is a schematic overall configuration diagram of a vehicle air conditioner according to a first embodiment. [Diagram 2] FIG. 2 is a perspective view of the compressor module of the first embodiment with a cover member removed. [Diagram 3] FIG. 2 is an external perspective view of the compressor module according to the first embodiment. [Figure 4] 2 is a block diagram showing an electric control unit of the vehicle air conditioner of the first embodiment. FIG. [Diagram 5] 1 is a schematic overall configuration diagram showing a flow of refrigerant in a hot gas heating mode of a vehicle air conditioner according to a first embodiment. FIG. [Figure 6] FIG. 5 is a schematic overall configuration diagram of a vehicle air conditioner according to a second embodiment. [Figure 7] FIG. 11 is a perspective view of a compressor module according to a second embodiment with a cover member removed. [Figure 8] FIG. 11 is a schematic overall configuration diagram of a vehicle air conditioner according to a third embodiment. [Figure 9] FIG. 11 is a perspective view of a compressor module according to a third embodiment with a cover member removed. [Figure 10] 10 is an external perspective view of the compressor module as viewed from the X direction in FIG. 9. [Figure 11] FIG. 11 is a schematic overall configuration diagram of a vehicle air conditioner according to a fourth embodiment. [Figure 12] FIG. 11 is a schematic overall configuration diagram of a vehicle air conditioner according to a fifth embodiment. [Figure 13] FIG. 13 is a perspective view of the compressor module of the fifth embodiment with a cover member removed. [Figure 14] FIG. 13 is an external perspective view of a compressor module according to a fifth embodiment. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0016] Hereinafter, a number of embodiments for carrying out the present invention 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 the 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 indicated, as long as there is no particular problem with the combination.

[0017] (First embodiment) A first embodiment of a compressor module according to the present invention will be described with reference to Figs. 1 to 5. A compressor module 100 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.

[0018] Specifically, the vehicle air conditioner 1 adjusts the temperature of a battery 80 as an in-vehicle device. The battery 80 is a secondary battery that stores power to be supplied to a plurality of in-vehicle devices that operate electrically. The battery 80 is an assembled battery formed by electrically connecting a plurality of stacked battery cells in series or parallel. The battery cells in this embodiment are lithium ion batteries.

[0019] The battery 80 generates heat during operation (i.e., during charging and discharging). The battery 80 has a characteristic that its output is likely to decrease at low temperatures and its deterioration is likely to progress at high temperatures. For this reason, the temperature of the battery 80 needs to be maintained within an appropriate temperature range (in this embodiment, 15° C. or higher and 55° C. or lower). Therefore, in the electric vehicle of this embodiment, the vehicle air conditioner 1 is used to adjust the temperature of the battery 80.

[0020] The vehicle air conditioner 1 includes a heat pump cycle 10, a low-temperature side heat medium circuit 30, an interior air conditioning unit 50, a control device 60, etc. The compressor module 100 is a component that integrates a plurality of components that mainly configure the heat pump cycle 10. In the compressor module 100 of this embodiment, the components surrounded by the dashed line in Fig. 1 are integrated.

[0021] More specifically, in the compressor module 100 of this embodiment, the components of the heat pump cycle 10, such as the compressor 11, the muffler section 12, the heating expansion valve 15a, the cooling expansion valve 15b, the cooling expansion valve 15c, the hot gas flow control valve 15d, the evaporation pressure control valve 19, the chiller 20, the accumulator section 21, the dehumidification on-off valve 23a, and the heating on-off valve 23b, are integrated together.

[0022] Among these components, the compressor 11, the heating expansion valve 15a, the cooling expansion valve 15b, the cooling expansion valve 15c, the hot gas flow rate control valve 15d, the evaporation pressure control valve 19, the chiller 20, the dehumidification on-off valve 23a, and the heating on-off valve 23b are attached to a flow path box 101 of the compressor module 100, which will be described later, and are integrated together. In addition, the muffler section 12 and the accumulator section 21 are formed integrally with the flow path box 101.

[0023] Therefore, the flow path box 101 is a mounting member for mounting a plurality of components. Furthermore, the flow path box 101 is a passage forming member in which a plurality of internal refrigerant passages for circulating the refrigerant of the heat pump cycle 10 and a plurality of internal heat medium passages for circulating the low-temperature side heat medium of the low-temperature side heat medium circuit 30 are formed. The detailed configuration of the compressor module 100 will be described later.

[0024] First, a description will be given of the heat pump cycle 10. The heat pump cycle 10 is a vapor compression type refrigeration cycle device that adjusts the temperature of the air blown into the vehicle cabin and the low-temperature side heat medium circulating through the low-temperature side heat medium circuit 30. The heat pump cycle 10 is configured to be able to switch the refrigerant circuit according to various operation modes described later for air conditioning in the vehicle cabin and cooling of on-board devices.

[0025] The heat pump cycle 10 employs an HFO refrigerant (specifically, R1234yf) as a 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. 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 cycle together with the refrigerant.

[0026] The compressor 11 draws in, compresses, and discharges the refrigerant in the heat pump cycle 10. The compressor 11 is an electric compressor that uses an electric motor to drive a fixed-capacity compression mechanism with a fixed discharge capacity. The rotation speed (i.e., refrigerant discharge capacity) of the compressor 11 is controlled by a control signal output from a control device 60, which will be described later. Therefore, the compressor 11 is an electric device that is operated by electricity.

[0027] A compressor-side inlet 101b formed in the flow path box 101 is connected to the discharge port of the compressor 11 via a high-pressure hose 11b. The high-pressure hose 11b has a multi-layered refrigerant hose portion in which an outer layer is made of a thermoplastic elastomer containing a base fabric and an inner layer is made of a resin that suppresses the permeation of the refrigerant. Therefore, the refrigerant hose portion of the high-pressure hose 11b is flexible and can be elastically deformed.

[0028] The compressor side inlet 101b is connected through an internal refrigerant passage to an inlet of a muffler section 12 formed in the flow path box 101. The muffler section 12 forms a buffer space into which the refrigerant discharged from the compressor 11 flows to reduce pressure pulsation of the discharged refrigerant. Therefore, the muffler section 12 is a high-pressure side refrigerant device into which the high-pressure side refrigerant flows.

[0029] An outlet of the muffler section 12 is connected to an inlet of the first internal three-way joint section 13a via an internal refrigerant passage. The first internal three-way joint section 13a is a part of a three-way joint structure formed by connecting a plurality of internal refrigerant passages formed inside the flow path box 101.

[0030] Furthermore, the second inner three-way joint portion 13b to the sixth inner three-way joint portion 13f are formed inside the flow path box 101 of this embodiment. The second inner three-way joint portion 13b to the sixth inner three-way joint portion 13f and the inner three-way joint portions described in the following embodiments all have the same basic configuration as the first inner three-way joint portion 13a.

[0031] These internal three-way joints function as a branching section that branches the flow of refrigerant flowing in from one inlet when one of the three inlet / outlets is used as an inlet and two are used as outlets, and as a merging section that merges the flow of refrigerant flowing in from the two inlets when two of the three inlet / outlets are used as inlets and one is used as an outlet.

[0032] Therefore, the first inner three-way joint portion 13a serves as a discharge-side branch portion that branches the flow of the refrigerant discharged from the compressor 11.

[0033] One of the outlets of the first internal three-way joint 13a is connected to a condenser-side outlet 101c formed in the flow path box 101. The other of the outlets of the first internal three-way joint 13a is connected to one of the inlets of the fourth internal three-way joint 13d via an internal refrigerant passage. The internal refrigerant passage extending from the other of the outlets of the first internal three-way joint 13a to one of the inlets of the fourth internal three-way joint 13d is the hot gas passage 22a.

[0034] A hot gas flow rate control valve 15d is disposed in the hot gas passage 22a. The hot gas flow rate control valve 15d is an electrically operated variable throttle mechanism that reduces the pressure of the refrigerant flowing through the hot gas passage 22a and adjusts the flow rate (mass flow rate) of the refrigerant flowing downstream during a hot gas heating mode, which will be described later.

[0035] The operation of the hot gas flow rate control valve 15d is controlled by a control signal (specifically, a control pulse) output from the control device 60. Therefore, the hot gas flow rate control valve 15d is an electric device. Furthermore, the hot gas flow rate control valve 15d has a full-closing function of fully closing the throttle passage to block the refrigerant passage.

[0036] The refrigerant inlet side of the indoor condenser 14 is connected to the condenser side outlet 101c. The indoor condenser 14 is disposed in an air conditioning case 51 of the indoor air conditioning unit 50. The indoor condenser 14 is a heat exchanger that exchanges heat between the refrigerant discharged from the compressor 11 and the blown air. The indoor condenser 14 heats the blown air by dissipating heat contained in the refrigerant discharged from the compressor 11 to the blown air, which is the fluid to be heated.

[0037] Therefore, the interior condenser 14 is a heating section that heats the blown air, which is the fluid to be heated, using one of the refrigerants branched at the first interior three-way joint portion 13a as a heat source.

[0038] A refrigerant outlet of the indoor condenser 14 is connected to a condenser-side inlet 101d formed in the flow path box 101. The condenser-side inlet 101d is connected to an inlet of the second internal three-way joint portion 13b via an internal refrigerant passage.

[0039] One of the outlets of the second internal three-way joint portion 13b is connected through an internal refrigerant passage to an outdoor unit side outlet 101e formed in the flow path box 101. The other of the outlets of the second internal three-way joint portion 13b is connected through an internal refrigerant passage to one of the inlets of the internal four-way joint portion 13x. The internal refrigerant passage extending from the other outlet of the second internal three-way joint portion 13b to the one of the inlets of the internal four-way joint portion 13x is the dehumidification passage 22b.

[0040] A dehumidification on-off valve 23a is disposed in the dehumidification passage 22b. The dehumidification on-off valve 23a is an on-off valve that opens and closes the dehumidification passage 22b. The dehumidification on-off valve 23a is an electromagnetic valve whose opening and closing operation is controlled by a control voltage output from the control device 60. Therefore, the dehumidification on-off valve 23a is an electric device.

[0041] The internal four-way joint portion 13x is a portion of a four-way joint structure formed by connecting a plurality of internal refrigerant passages formed inside the flow path box 101. Such an internal four-way joint portion may be formed by combining a plurality of internal three-way joint portions.

[0042] A heating expansion valve 15a is disposed in the internal refrigerant passage extending from one outlet of the second internal three-way joint portion 13b to the outdoor unit side outlet 101e. The heating expansion valve 15a is an outdoor unit pressure reducing portion that reduces the pressure of the refrigerant flowing out from one outlet of the second internal three-way joint portion 13b and adjusts the flow rate of the refrigerant flowing out to the downstream side during a heating mode, which will be described later.

[0043] The basic configuration of the heating expansion valve 15a is the same as that of the hot gas flow rate control valve 15d. Therefore, the heating expansion valve 15a is an electric device. Furthermore, the heating expansion valve 15a has a full-open function that functions as a simple refrigerant passage by fully opening the throttle passage, with almost no flow rate control action or refrigerant pressure reduction action.

[0044] The outdoor unit side outlet 101e is connected to the refrigerant inlet side of the outdoor heat exchanger 16. The outdoor heat exchanger 16 is a heat exchanger that exchanges heat between the refrigerant flowing out from the heating expansion valve 15a and the outside air blown by a cooling fan (not shown). The outdoor heat exchanger 16 is disposed on the front side of the drive unit room.

[0045] The drive unit compartment is formed at the front side of the vehicle interior and forms a space in which at least a part of the equipment for generating the driving force for traveling (e.g., a motor generator) is disposed. Therefore, when the vehicle is traveling, the traveling wind that flows into the drive unit compartment through a grill or the like can be directed at the exterior heat exchanger 16.

[0046] A refrigerant outlet of the outdoor heat exchanger 16 is connected to an outdoor unit side inlet 101f formed in the flow path box 101. The outdoor unit side inlet 101f is connected to an inlet of the third internal three-way joint portion 13c via an internal refrigerant passage.

[0047] One of the outlets of the third internal three-way joint portion 13c is connected to the other inlet of the internal four-way joint portion 13x via an internal refrigerant passage. A first check valve 17a is disposed in the internal refrigerant passage extending from one of the outlets of the third internal three-way joint portion 13c to the other inlet of the internal four-way joint portion 13x.

[0048] The first check valve 17a allows the refrigerant to flow from the third internal three-way joint portion 13c side to the internal four-way joint portion 13x side, and prohibits the refrigerant from flowing from the internal four-way joint portion 13x side to the third internal three-way joint portion 13c side.

[0049] The other outlet of the third internal three-way joint 13c is connected to one inlet of the sixth internal three-way joint 13f via an internal refrigerant passage. The internal refrigerant passage extending from the other outlet of the third internal three-way joint 13c to one inlet of the sixth internal three-way joint 13f is the heating passage 22c.

[0050] The heating on-off valve 23b and the second check valve 17b are arranged in the heating passage 22c. The heating on-off valve 23b is an on-off valve that opens and closes the heating passage 22c. The basic configuration of the heating on-off valve 23b is the same as that of the dehumidification on-off valve 23a. Therefore, the heating on-off valve 23b is an electric device.

[0051] Here, the dehumidifying on-off valve 23a and the heating on-off valve 23b can switch the refrigerant circuit by opening and closing the internal refrigerant passages. Therefore, the dehumidifying on-off valve 23a and the heating on-off valve 23b are refrigerant circuit switching units.

[0052] In addition, the second check valve 17b allows the refrigerant to flow from the heating on-off valve 23b side to the sixth internal three-way joint portion 13f side, and prohibits the refrigerant from flowing from the sixth internal three-way joint portion 13f side to the heating on-off valve 23b side.

[0053] One outlet of the internal four-way joint 13x is connected to an evaporator-side outlet 101g formed in the flow path box 101 via an internal refrigerant passage. The other outlet of the internal four-way joint 13x is connected to the other inlet of the fourth internal three-way joint 13d via an internal refrigerant passage. The outlet of the fourth internal three-way joint 13d is connected to a chiller-side outlet 101i formed in the flow path box 101 via an internal refrigerant passage.

[0054] A cooling expansion valve 15b is disposed in the internal refrigerant passage extending from one outlet of the internal four-way joint 13x to the evaporator-side outlet 101g. The cooling expansion valve 15b is an evaporator pressure reducing section that reduces the pressure of the refrigerant flowing out from one outlet of the internal four-way joint 13x and adjusts the flow rate of the refrigerant flowing out downstream during a cooling mode, which will be described later.

[0055] The cooling expansion valve 15b has a basic configuration similar to that of the heating expansion valve 15a, and is therefore an electric device.

[0056] The refrigerant inlet side of the interior evaporator 18 is connected to the evaporator side outlet 101g. The interior evaporator 18 is disposed in an air conditioning case 51 of the interior air conditioning unit 50. The interior evaporator 18 is a heat exchanger that exchanges heat between the low-pressure refrigerant decompressed by the cooling expansion valve 15b and the ventilation air blown into the vehicle cabin. The interior evaporator 18 evaporates the low-pressure refrigerant to exert a heat absorption effect, thereby cooling the ventilation air.

[0057] The refrigerant outlet of the indoor evaporator 18 is connected to an evaporator-side inlet 101h formed in the flow path box 101. The evaporator-side inlet 101h is connected to one inlet of the fifth internal three-way joint portion 13e via an internal refrigerant passage.

[0058] An evaporation pressure regulating valve 19 is disposed in the internal refrigerant passage extending from the evaporator-side inlet 101h to one inlet of the fifth internal three-way joint portion 13e.

[0059] The evaporation pressure regulating valve 19 is an electric variable throttle mechanism that changes the valve opening so as to maintain the refrigerant evaporation pressure in the indoor evaporator 18 at or above a predetermined set pressure (saturation pressure at 1°C in this embodiment) in order to suppress frost formation on the indoor evaporator 18. The basic configuration of the evaporation pressure regulating valve 19 is similar to that of the heating expansion valve 15a. Therefore, the evaporation pressure regulating valve 19 is an electric device.

[0060] A cooling expansion valve 15c is disposed in the internal refrigerant passage extending from the other outlet of the internal four-way joint 13x to the other inlet of the fourth internal three-way joint 13d. The cooling expansion valve 15c is a chiller pressure reducing section that reduces the pressure of the refrigerant flowing out from the other outlet of the internal four-way joint 13x and adjusts the flow rate of the refrigerant flowing out downstream during a single cooling mode, which will be described later.

[0061] The basic configuration of the cooling expansion valve 15c is similar to that of the cooling expansion valve 15b, and therefore the cooling expansion valve 15c is an electric device.

[0062] Here, the heating expansion valve 15a, the cooling expansion valve 15b, the cooling expansion valve 15c, and the hot gas flow rate control valve 15d have a fully closing function. These electric variable throttle mechanisms can switch the refrigerant circuit by exerting the fully closing function. Therefore, the cooling expansion valve 15b, the cooling expansion valve 15c, and the hot gas flow rate control valve 15d also function as a refrigerant circuit switching unit.

[0063] The chiller-side outlet 101i is directly connected to a refrigerant inlet of the chiller 20. The chiller 20 is a heat exchanger that exchanges heat between the low-pressure side refrigerant decompressed by the cooling expansion valve 15c and the low-temperature side heat medium circulating through the low-temperature side heat medium circuit 30. The chiller 20 cools the low-temperature side heat medium by evaporating the low-pressure side refrigerant and exerting a heat absorption effect.

[0064] A chiller-side inlet 101j formed in the flow path box 101 is directly connected to the refrigerant outlet of the chiller 20. The chiller-side inlet 101j is connected to the other inlet of the fifth internal three-way joint portion 13e. The outlet of the fifth internal three-way joint portion 13e is connected to the other inlet of the sixth internal three-way joint portion 13f via an internal refrigerant passage.

[0065] An outlet of the sixth internal three-way joint 13f is connected to an inlet side of the accumulator 21 via an internal refrigerant passage. The accumulator 21 is a low-pressure side gas-liquid separator that separates the refrigerant that has flowed into it into gas and liquid and stores the excess liquid-phase refrigerant in the cycle. An outlet of the accumulator 21 is connected to a compressor-side outlet 101a formed in the flow path box 101 via an internal refrigerant passage.

[0066] The compressor-side outlet 101a is connected to the suction port of the compressor 11 via a low-pressure hose 11a. The basic configuration of the low-pressure hose 11a is similar to that of the high-pressure hose 11b. Therefore, the refrigerant hose portion of the low-pressure hose 11a is flexible and can be elastically deformed.

[0067] Next, a detailed configuration of the compressor module 100 will be described with reference to Figures 2 and 3. As shown in Figures 2 and 3, the compressor module 100 includes a flow path box 101 and a cover member 102. The flow path box 101 is made of metal (aluminum alloy in this embodiment). The cover member 102 is made of resin (polypropylene in this embodiment) that has better soundproofing performance than metal.

[0068] The cover member 102 is attached to the flow path box 101 by means of bolts or the like. With the cover member 102 attached to the flow path box 101, the compressor module 100 has an external appearance of a rectangular parallelepiped shape, as shown in Fig. 3. Of the six outer surfaces of the rectangular parallelepiped shape of the compressor module 100, three faces are formed by the flow path box 101. The remaining three faces are formed by the cover member 102.

[0069] The cover member 102 is attached to the flow path box 101, thereby forming, together with the flow path box 101, an accommodation space 103 for accommodating the compressor 11 and the like inside the compressor module 100. A seal member (not shown) is interposed at the contact portion between the flow path box 101 and the cover member 102. Therefore, the accommodation space 103 is formed as a sealed space into which air does not flow in from the outside or out to the outside.

[0070] A heat insulating material 104 is disposed over almost the entire outer surface of the compressor module 100. The heat insulating material 104 is a heat insulating portion that suppresses heat transfer between the air in the accommodation space 103 and the outside air. As the heat insulating material 104, a fiber-based heat insulating material such as glass wool, a foam-based heat insulating material such as urethane foam, or the like can be used.

[0071] The storage space 103 accommodates the compressor 11, the heating expansion valve 15a, the cooling expansion valve 15b, the cooling expansion valve 15c, the hot gas flow control valve 15d, the evaporation pressure control valve 19, the chiller 20, the dehumidification opening / closing valve 23a, the heating opening / closing valve 23b, etc.

[0072] For this reason, compressor side outlet 101a, compressor side inlet 101b, chiller side outlet 101i, and chiller side inlet 101j are formed inside storage space 103. More specifically, compressor side outlet 101a and compressor side inlet 101b are formed on the inner side surface of flow path box 101 facing storage space 103, and are thereby formed inside storage space 103.

[0073] Moreover, the indoor condenser 14, the outdoor heat exchanger 16, and the indoor evaporator 18 are disposed outside the accommodation space 103. Therefore, the indoor condenser 14, the outdoor heat exchanger 16, and the indoor evaporator 18 in this embodiment are external components.

[0074] The condenser side outlet 101c, the condenser side inlet 101d, the outdoor unit side outlet 101e, the outdoor unit side inlet 101f, the evaporator side outlet 101g, and the evaporator side inlet 101h are formed on the outer surface of the flow path box 101, and thereby are formed outside the storage space 103.

[0075] Therefore, in this embodiment, the condenser side outlet 101c, the condenser side inlet 101d, the outdoor unit side outlet 101e, the outdoor unit side inlet 101f, the evaporator side outlet 101g, and the evaporator side inlet 101h are external connection ports to which the inlet and outlet sides of external component equipment are connected.

[0076] Further, a plurality of (four in this embodiment) fixing portions 101s for fixing the compressor 11 are formed on the bottom surface that forms the accommodation space 103 of the flow path box 101. The compressor 11 is fixed to the fixing portions 101s via vibration-proof rubber 11c. The vibration-proof rubber 11c is a vibration-proof member that suppresses the vibration of the compressor 11 from being transmitted to the flow path box 101.

[0077] More specifically, the vibration-proof rubber 11c is formed by adhering metal bolt-shaped fastening members with excellent heat transfer properties to both end faces of a substantially cylindrical thermoplastic elastomer. Therefore, when the fastening members of the vibration-proof rubber 11c are fastened to the compressor 11, the heat of the compressor 11 is transferred to the vibration-proof rubber 11c, and the vibration-proof rubber 11c can be heated. In other words, the vibration-proof rubber 11c is arranged so that it can be heated by the heat generated by the compressor 11.

[0078] As shown in FIG. 2, the low-pressure hose 11a and the high-pressure hose 11b are attached to the compressor 11 and the flow path box 101 in a curved state.

[0079] The heating expansion valve 15a, the cooling expansion valve 15b, the cooling expansion valve 15c, the hot gas flow rate control valve 15d, the evaporation pressure control valve 19, the dehumidification on-off valve 23a, and the heating on-off valve 23b are fixed by means of screw fastening, press fitting, or the like, in mounting holes formed in the flow path box 101. The mounting holes communicate with the internal refrigerant passages.

[0080] In addition, chiller 20 is fixed to flow path box 101 by fitting the refrigerant inlet / outlet and heat medium inlet / outlet formed to protrude to the outside into the refrigerant inlet / outlet (i.e., chiller side outlet 101i, chiller side inlet 101j) and heat medium inlet / outlet formed in flow path box 101, respectively.

[0081] In addition, the muffler section 12 is formed in a shape that bulges out toward the accommodation space 103 in order to form a buffer space. The muffler section 12 in this embodiment is disposed on a side surface of the flow path box 101.

[0082] Moreover, the electric device accommodated in the accommodation space 103 is connected to the control device 60 arranged outside the accommodation space 103 via a sealed terminal (so-called hermetic seal terminal) not shown.

[0083] Next, the low-temperature side heat medium circuit 30 will be described. The low-temperature side heat medium circuit 30 is a heat medium circuit that circulates a low-temperature side heat medium. In the low-temperature side heat medium circuit 30, an ethylene glycol aqueous solution is used as the low-temperature side heat medium. As shown in FIG. 1, the low-temperature side heat medium circuit 30 is connected to a low-temperature side pump 31, a coolant passage 80a of a battery 80, a heat medium passage of the chiller 20 of the compressor module 100, and the like.

[0084] The low-temperature side pump 31 is a low-temperature side heat medium pumping section that draws in and pumps the low-temperature side heat medium. The low-temperature side pump 31 pumps the low-temperature side heat medium flowing out from the cooling water passage 80a of the battery 80 to a low-temperature side heat medium inlet 101m formed in the flow path box 101 of the compressor module 100. The low-temperature side 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 60, and is included in the electric equipment.

[0085] The low-temperature side heat medium inlet 101m is connected through an internal heat medium passage to an inlet of the heat medium passage of the chiller 20. The outlet of the heat medium passage of the chiller 20 is connected through an internal heat medium passage to a low-temperature side heat medium outlet 101n formed in the flow path box 101.

[0086] The inlet side of the cooling water passage 80a of the battery 80 is connected to the low-temperature side heat medium outlet 101n. The cooling water passage 80a of the battery 80 is formed inside a dedicated battery case that houses multiple battery cells arranged in a stacked manner. The cooling water passage 80a has a passage configuration in which multiple passages are connected in parallel inside the dedicated battery case. This allows the cooling water passage 80a to cool all the battery cells evenly. The suction port side of the low-temperature side pump 31 is connected to the outlet of the cooling water passage 80a.

[0087] Next, the interior air conditioning unit 50 will be described. The interior air conditioning unit 50 is a unit that integrates a number of components to blow air adjusted to an appropriate temperature for air conditioning the vehicle interior to an appropriate location within the vehicle interior. The interior air conditioning unit 50 is disposed inside the instrument panel at the front end of the vehicle interior.

[0088] 1, the indoor air-conditioning unit 50 is formed by accommodating an indoor blower 52, an indoor evaporator 18, an indoor condenser 14, etc. in an air-conditioning case 51 that forms an air passage for blown air. The air-conditioning case 51 is molded from a resin (e.g., polypropylene) that has a certain degree of elasticity and excellent strength.

[0089] An inside / outside air switching device 53 is disposed on the most upstream side of the blown air flow of the air conditioning case 51. The inside / outside air switching device 53 switches between introducing inside air (i.e., air inside the vehicle cabin) and outside air (i.e., air outside the vehicle cabin) into the air conditioning case 51. The operation of the inside / outside air switching device 53 is controlled by a control signal output from the control device 60.

[0090] An interior blower 52 is disposed downstream of the inside / outside air switching device 53 in the flow of blown air. The interior blower 52 blows the air drawn in through the inside / outside air switching device 53 toward the vehicle interior. The rotation speed (i.e., blowing capacity) of the interior blower 52 is controlled by a control voltage output from the control device 60.

[0091] The indoor evaporator 18 and the indoor condenser 14 are disposed downstream in the flow of air blown by the indoor blower 52. The indoor evaporator 18 is disposed upstream in the flow of air blown by the indoor condenser 14. A cold air bypass passage 55 is formed in the air conditioning case 51, which allows the blown air after passing through the indoor evaporator 18 to flow around the indoor condenser 14.

[0092] An air mix door 54 is disposed downstream of the indoor evaporator 18 in the air conditioning case 51 in terms of the blown air flow and upstream of the indoor condenser 14 and the cold air bypass passage 55 in terms of the blown air flow.

[0093] The air mix door 54 adjusts the ratio of the volume of the blown air passing through the indoor condenser 14 side to the volume of the blown air passing through the cold air bypass passage 55, among the blown air after passing through the indoor evaporator 18. The operation of the actuator for driving the air mix door 54 is controlled by a control signal output from the control device 60.

[0094] A mixing space 56 is disposed downstream of the indoor condenser 14 and the cold air bypass passage 55 in the flow of blown air. The mixing space 56 is a space in which the blown air heated by the indoor condenser 14 and the blown air that has passed through the cold air bypass passage 55 and has not been heated are mixed.

[0095] Therefore, in the interior air conditioning unit 50, by adjusting the opening degree of the air mix door 54, it is possible to adjust the temperature of the blown air (that is, the conditioned air) that is mixed in the mixing space 56 and blown into the vehicle interior.

[0096] At the most downstream part of the blown air flow of the air conditioning case 51, a plurality of openings (not shown) are formed for blowing out the conditioned air toward various parts in the vehicle cabin. A blow mode door (not shown) for opening and closing each of the openings is disposed in each of the openings. The operation of the actuator for driving the blow mode door is controlled by a control signal output from the control device 60.

[0097] Therefore, in the interior air conditioning unit 50, by switching the opening hole that the blowing mode door opens and closes, conditioned air that has been adjusted to an appropriate temperature can be blown out to an appropriate location in the vehicle cabin.

[0098] Next, the electric control unit of this embodiment will be described. The control device 60 has a well-known microcomputer including a CPU, ROM, RAM, etc., and its peripheral circuits. The control device 60 performs various calculations and processing based on a control program stored in the ROM. Then, the control device 60 controls the operation of various control target devices 11, 15a to 15d, 19, 23a, 23b, 31, 52, 53, etc. connected to the output side based on the calculation and processing results.

[0099] As shown in the block diagram of FIG. 4, an inside air temperature sensor 61a, an outside air temperature sensor 61b, a solar radiation sensor 61c, a discharge refrigerant temperature and pressure sensor 62a, a high-pressure side refrigerant temperature and pressure sensor 62b, an outdoor unit side refrigerant temperature and pressure sensor 62c, an evaporator side refrigerant temperature and pressure sensor 62d, a chiller side refrigerant temperature and pressure sensor 62e, a low-temperature side heat medium temperature sensor 63a, a battery temperature sensor 64, an air conditioning air temperature sensor 65, etc. are connected to the input side of the control device 60.

[0100] Detection signals from these control sensors are input to the control device 60. These sensors are included in the components of the heat pump cycle device 1. These sensors output electrical signals, and therefore are all included in the category of electric devices.

[0101] The inside air temperature sensor 61a is an inside air temperature detector that detects the temperature inside the vehicle cabin (inside air temperature) Tr. The outside air temperature sensor 61b is an outside air temperature detector that detects the temperature outside the vehicle cabin (outside air temperature) Tam. The solar radiation sensor 61c is an solar radiation amount detector that detects the amount of solar radiation As irradiated into the vehicle cabin.

[0102] The discharge refrigerant temperature and pressure sensor 62a is a discharge refrigerant temperature and pressure detection unit that detects the discharge refrigerant temperature Td and the discharge refrigerant pressure Pd of the refrigerant discharged from the compressor 11. The discharge refrigerant temperature and pressure sensor 62a in this embodiment is attached to a housing portion that forms the outer shell of the compressor 11. Therefore, the discharge refrigerant temperature and pressure sensor 62a is disposed in the accommodation space 103 of the compressor module 100.

[0103] The high-pressure side refrigerant temperature and pressure sensor 62b is a high-pressure side refrigerant temperature and pressure detection unit that detects the high-pressure side refrigerant temperature T1 and high-pressure side refrigerant pressure P1 of the refrigerant flowing out from the indoor condenser 14. The outdoor unit side refrigerant temperature and pressure sensor 62c detects the outdoor unit side refrigerant temperature T2 and outdoor unit side refrigerant pressure P2 of the refrigerant flowing out from the outdoor heat exchanger 16.

[0104] The evaporator side refrigerant temperature and pressure sensor 62d is an evaporator side refrigerant temperature and pressure detection unit that detects the evaporator side refrigerant temperature Te and evaporator side refrigerant pressure Pe of the refrigerant flowing out from the indoor evaporator 18. The chiller side refrigerant temperature and pressure sensor 62e is a chiller side refrigerant temperature and pressure detection unit that detects the chiller side refrigerant temperature Tc and chiller side refrigerant pressure Pc of the refrigerant flowing out from the refrigerant passage of the chiller 20.

[0105] The discharge refrigerant temperature and pressure sensor 62a, the high pressure side refrigerant temperature and pressure sensor 62b, the outdoor unit side refrigerant temperature and pressure sensor 62c, the evaporator side refrigerant temperature and pressure sensor 62d, and the chiller side refrigerant temperature and pressure sensor 62e are attached to the flow path box 101 of the compressor module 100. Furthermore, the sensors arranged in the accommodation space 103 are connected to the control device 60 via sealed terminals (not shown), similar to the compressor 11 and the like.

[0106] In addition, in this embodiment, a detection unit in which the pressure detection unit and the temperature detection unit are integrated is used as the refrigerant temperature pressure sensor, but of course, a pressure detection unit and a temperature detection unit that are each configured as separate units may also be used.

[0107] The low-temperature side heat medium temperature sensor 63a is a low-temperature side heat medium temperature detection unit that detects the low-temperature side heat medium temperature TWL, which is the temperature of the low-temperature side heat medium flowing into the coolant passage 80a of the battery 80.

[0108] The battery temperature sensor 64 is a battery temperature detection unit that detects the battery temperature TB, which is the temperature of the battery 80. The battery temperature sensor 64 has multiple temperature sensors and detects the temperatures at multiple locations of the battery 80. Therefore, the control device 60 can detect the temperature difference and temperature distribution of each battery cell that forms the battery 80. Furthermore, the average value of the detection values ​​of the multiple temperature sensors is used as the battery temperature TB.

[0109] The conditioned air temperature sensor 65 is an conditioned air temperature detection unit that detects the temperature TAV of the air blown from the mixing space 56 into the vehicle interior.

[0110] Furthermore, an operation panel 70 disposed near the instrument panel at the front of the vehicle interior is connected to the input side of the control device 60 as shown in Fig. 4. Operation signals are input to the control device 60 from various operation switches provided on the operation panel 70.

[0111] The various operation switches provided on the operation panel 70 specifically include an auto switch, an air conditioner switch, an air volume setting switch, a temperature setting switch, and the like.

[0112] The auto switch is an operational switch for setting or canceling the automatic control operation of the vehicle air conditioner 1. The air conditioner switch is an operational switch for requesting cooling of the blown air by the interior evaporator 18. The air volume setting switch is an operational switch for manually setting the air volume of the interior blower 52. The temperature setting switch is an operational switch for setting the set temperature Tset in the vehicle cabin.

[0113] The control device 60 of this embodiment is an integrated unit that controls various controlled devices connected to its output side. Therefore, the configuration (hardware and software) that controls the operation of each controlled device constitutes a control unit that controls the operation of each controlled device. For example, the configuration of the control device 60 that controls the refrigerant discharge capacity (specifically, the rotation speed) of the compressor 11 constitutes a discharge capacity control unit 60a.

[0114] Next, the operation of the vehicle air conditioner 1 of this embodiment configured as described above will be described. In the vehicle air conditioner 1 of this embodiment, various operation modes are switched in order to condition the air in the vehicle compartment and adjust the temperature of the battery 80. The operation modes are switched by executing a control program stored in advance in the control device 60.

[0115] The control program is executed not only when the so-called IG switch is turned on and the vehicle system is running, but also when the battery 80 is being charged from an external power source. The control program reads detection signals from the above-mentioned sensors and operation signals from the operation switches of the operation panel 70 at predetermined intervals. Then, the driving mode is switched based on the read detection signals and operation signals.

[0116] Furthermore, in the control program of this embodiment, when the auto switch on the operation panel 70 is turned on and automatic control operation of the vehicle interior air conditioning is set, a target outlet temperature TAO, which is the target temperature of the blown air into the vehicle interior, is calculated based on the read detection signal and operation signal.

[0117] The target air outlet temperature TAO is calculated using the following formula F1. TAO=Kset×Tset-Kr×Tr-Kam×Tam-Ks×As+C…(F1) Here, Tset is the set temperature in the vehicle cabin set by the temperature setting switch on the operation panel 70. Tr is the inside air temperature detected by the inside air temperature sensor 61a. Tam is the outside air temperature detected by the outside air temperature sensor 61b. As is the amount of solar radiation detected by the solar radiation sensor 61c. Kset, Kr, Kam, and Ks are control gains, and C is a correction constant. The operation of each driving mode will be described in detail below.

[0118] (a) Cooling mode The cooling mode is an operation mode in which cooled air is blown into the vehicle cabin to cool the vehicle cabin. In the control program of this embodiment, the operation mode for cooling the vehicle cabin is executed mainly when the outside air temperature Tam is relatively high, such as in summer.

[0119] The cooling modes include a single cooling mode in which the vehicle cabin is cooled without cooling the battery 80, and a cooling and cooling mode in which the vehicle cabin is cooled while cooling the battery 80. In the control program of this embodiment, when the battery temperature TB becomes equal to or higher than a predetermined reference upper limit temperature KTBH, an operation mode for cooling the battery 80, which is an in-vehicle device, is executed.

[0120] (a-1) Single cooling mode In the heat pump cycle 10 in the cooling only mode, the control device 60 fully opens the heating expansion valve 15a, fully closes the cooling expansion valve 15b, fully closes the cooling expansion valve 15c, and fully closes the hot gas flow control valve 15d. The control device 60 also closes the dehumidification opening / closing valve 23a and the heating opening / closing valve 23b.

[0121] For this reason, in the heat pump cycle 10 in the cooling only mode, the refrigerant discharged from the compressor 11 is switched to a refrigerant circuit in which it circulates in the following order: the muffler section 12, the indoor condenser 14, the heating expansion valve 15a which is in a fully open state, the outdoor heat exchanger 16, the cooling expansion valve 15b which is in a throttled state, the indoor evaporator 18, the evaporation pressure control valve 19, the accumulator section 21, and the suction port of the compressor 11.

[0122] In addition, in the indoor air conditioning unit 50 in the single cooling mode, the opening degree of the air mix door 54 is controlled so that the blowing air temperature TAV detected by the air conditioning air temperature sensor 65 approaches the target blowing temperature TAO. In addition, in the indoor air conditioning unit 50 in the single cooling mode, the operation of the inside / outside air switching device 53 and the blowing mode door is controlled based on the target blowing temperature TAO. In addition, the control device 60 appropriately controls the operation of other controlled devices.

[0123] Therefore, in the heat pump cycle 10 in the cooling only mode, a vapor compression refrigeration cycle is configured in which the indoor condenser 14 and the outdoor heat exchanger 16 function as condensers that condense the refrigerant by dissipating heat, and the indoor evaporator 18 functions as an evaporator that evaporates the refrigerant.

[0124] In the interior air conditioning unit 50 in the single cooling mode, the blown air blown from the interior blower 52 is cooled by the interior evaporator 18. The blown air cooled by the interior evaporator 18 is reheated by the interior condenser 14 so as to approach the target blown air temperature TAO according to the opening degree of the air mix door 54. Then, the temperature-adjusted blown air is blown into the vehicle cabin, thereby cooling the vehicle cabin.

[0125] (a-2) Cooling mode In the heat pump cycle 10 in the cooling / air-cooling mode, the control device 60 controls the cooling expansion valve 15c to be in the throttling state, in contrast to the single cooling mode.

[0126] Therefore, in the heat pump cycle 10 in the cooling / cooling mode, the refrigerant discharged from the compressor 11 circulates in the same manner as in the single cooling mode. At the same time, the refrigerant discharged from the compressor 11 is switched to a refrigerant circuit in which it circulates in the order of the muffler section 12, the indoor condenser 14, the heating expansion valve 15a in a fully open state, the outdoor heat exchanger 16, the cooling expansion valve 15c in a throttled state, the chiller 20, the accumulator section 21, and the suction port of the compressor 11. In other words, the indoor evaporator 18 and the chiller 20 are switched to a refrigerant circuit in which they are connected in parallel with respect to the flow of the refrigerant.

[0127] In the low-temperature side heat medium circuit 30 in the cooling / air-cooling mode, the control device 60 operates the low-temperature side pump 31 to exert a predetermined reference pumping capacity. Therefore, in the low-temperature side heat medium circuit 30, the low-temperature side heat medium pumped by the low-temperature side pump 31 circulates through the heat medium passage of the chiller 20, the cooling water passage 80a of the battery 80, and the suction port of the low-temperature side pump 31 in that order.

[0128] In the indoor air conditioning unit 50 in the cooling / cooling mode, the opening degree of the air mix door 54, the inside / outside air switching device 53, and the operation of the blowing mode door are controlled in the same manner as in the single cooling mode. In addition, the control device 60 appropriately controls the operation of other control target devices.

[0129] Therefore, in the heat pump cycle 10 in the cooling / air-conditioning mode, a vapor compression refrigeration cycle is configured in which the indoor condenser 14 and the outdoor heat exchanger 16 function as condensers, and the indoor evaporator 18 and the chiller 20 function as evaporators.

[0130] In the low-temperature side heat medium circuit 30 in the cooling / air-cooling mode, the low-temperature side heat medium pumped from the low-temperature side pump 31 flows into the chiller 20 and is cooled. Then, the low-temperature side heat medium cooled in the chiller 20 flows through the coolant passage 80a of the battery 80, thereby cooling the battery 80.

[0131] In the interior air conditioning unit 50 in the cooling / air-conditioning mode, temperature-adjusted air is blown into the vehicle compartment, thereby cooling the vehicle compartment, similarly to the single cooling mode.

[0132] (b) Series dehumidification and heating mode The serial dehumidifying and heating mode is an operation mode in which the cooled and dehumidified blown air is reheated and blown into the vehicle cabin to dehumidify and heat the vehicle cabin. In the control program of this embodiment, when the outside air temperature Tam is in an intermediate temperature range in which the cooling mode or the heating mode is difficult to select, the operation mode for dehumidifying and heating the vehicle cabin is executed.

[0133] The series dehumidifying and heating modes include a single series dehumidifying and heating mode in which the vehicle interior is dehumidified and heated without cooling the battery 80, and a cooling series dehumidifying and heating mode in which the battery 80 is cooled and the vehicle interior is dehumidified and heated.

[0134] (b-1) Single series dehumidification and heating mode In the heat pump cycle 10 in the single series dehumidification heating mode, the controller 60 throttles the heating expansion valve 15a, throttles the cooling expansion valve 15b, fully closes the cooling expansion valve 15c, and fully closes the hot gas flow control valve 15d. The controller 60 also closes the dehumidification opening / closing valve 23a and the heating opening / closing valve 23b.

[0135] For this reason, in the heat pump cycle 10 in the single-serial dehumidification heating mode, the refrigerant discharged from the compressor 11 is switched to a refrigerant circuit in which it circulates in the following order: the muffler section 12, the indoor condenser 14, the heating expansion valve 15a which is in a throttling state, the outdoor heat exchanger 16, the cooling expansion valve 15b which is in a throttling state, the indoor evaporator 18, the evaporation pressure control valve 19, the accumulator section 21, and the suction port of the compressor 11.

[0136] In the indoor air conditioning unit 50 in the single series dehumidifying and heating mode, the opening degree of the air mix door 54, the inside / outside air switching device 53, and the operation of the blowing mode door are controlled in the same manner as in the single cooling mode. In addition, the control device 60 appropriately controls the operation of other control target devices.

[0137] Therefore, in the heat pump cycle 10 in the single series dehumidifying and heating mode, a vapor compression refrigeration cycle is configured in which the indoor condenser 14 functions as a condenser and the indoor evaporator 18 functions as an evaporator.

[0138] Furthermore, in the single series dehumidifying and heating mode, when the saturation temperature of the refrigerant in the outdoor heat exchanger 16 is higher than the outdoor air temperature Tam, the outdoor heat exchanger 16 functions as a condenser. When the saturation temperature of the refrigerant in the outdoor heat exchanger 16 is lower than the outdoor air temperature Tam, the outdoor heat exchanger 16 functions as an evaporator.

[0139] In the interior air conditioning unit 50 in the single serial dehumidifying and heating mode, the blown air blown from the interior blower 52 is cooled and dehumidified in the interior evaporator 18. The blown air cooled and dehumidified in the interior evaporator 18 is reheated in the interior condenser 14 so as to approach the target blown air temperature TAO according to the opening degree of the air mix door 54. Then, the temperature-adjusted blown air is blown into the vehicle cabin, thereby realizing dehumidifying and heating the vehicle cabin.

[0140] (b-2) Cooling series dehumidification heating mode In the heat pump cycle 10 in the cooling series dehumidification heating mode, the controller 60 controls the cooling expansion valve 15c to the throttling state, unlike in the single series dehumidification heating mode.

[0141] Therefore, in the heat pump cycle 10 in the cooling serial dehumidification heating mode, the refrigerant discharged from the compressor 11 circulates in the same manner as in the single serial dehumidification heating mode. At the same time, the refrigerant discharged from the compressor 11 is switched to a refrigerant circuit in which it circulates in the order of the muffler section 12, the indoor condenser 14, the heating expansion valve 15a in the throttling state, the outdoor heat exchanger 16, the cooling expansion valve 15c in the throttling state, the chiller 20, the accumulator section 21, and the suction port of the compressor 11. In other words, the indoor evaporator 18 and the chiller 20 are switched to a refrigerant circuit in which they are connected in parallel with respect to the flow of the refrigerant.

[0142] In the cooling serial dehumidification heating mode, the operation of the low-temperature side pump 31 is controlled in the same manner as in the cooling cooling mode. Therefore, in the low-temperature side heat medium circuit 30 in the cooling serial dehumidification heating mode, the low-temperature side heat medium circulates in the same manner as in the cooling cooling mode.

[0143] In the indoor air conditioning unit 50 in the cooling serial dehumidification heating mode, the opening degree of the air mix door 54, the inside / outside air switching device 53, and the operation of the blowing mode door are controlled in the same manner as in the single cooling mode. In addition, the control device 60 appropriately controls the operation of other control target devices.

[0144] Therefore, in the heat pump cycle 10 in the cooling serial dehumidification heating mode, a vapor compression refrigeration cycle is configured in which the indoor condenser 14 functions as a condenser, and the indoor evaporator 18 and the chiller 20 function as evaporators.

[0145] Furthermore, in the cooling serial dehumidification heating mode, similarly to the single serial dehumidification heating mode, when the saturation temperature of the refrigerant in the outdoor heat exchanger 16 is higher than the outdoor air temperature Tam, the outdoor heat exchanger 16 is made to function as a condenser. On the other hand, when the saturation temperature of the refrigerant in the outdoor heat exchanger 16 is lower than the outdoor air temperature Tam, the outdoor heat exchanger 16 is made to function as an evaporator.

[0146] In the low-temperature side heat medium circuit 30 in the cooling serial dehumidification heating mode, the low-temperature side heat medium cooled in the chiller 20 flows through the coolant passage 80a of the battery 80, thereby cooling the battery 80, as in the cooling and air-conditioning mode.

[0147] In the interior air conditioning unit 50 in the cooling series dehumidification heating mode, similarly to the single series dehumidification heating mode, temperature-adjusted ventilation air is blown into the vehicle compartment, thereby realizing dehumidification and heating of the vehicle compartment.

[0148] (c) Parallel dehumidification and heating mode The parallel dehumidifying and heating mode is an operating mode in which the cooled and dehumidified blown air is reheated with a heating capacity higher than that in the series dehumidifying and heating mode and blown into the passenger compartment, thereby performing dehumidifying and heating for the passenger compartment.

[0149] The parallel dehumidifying and heating modes include a single parallel dehumidifying and heating mode in which the vehicle interior is dehumidified and heated without cooling the battery 80, and a cooling / parallel dehumidifying and heating mode in which the battery 80 is cooled and the vehicle interior is dehumidified and heated.

[0150] (c-1) Single parallel dehumidification and heating mode In the heat pump cycle 10 in the single-parallel dehumidification heating mode, the control device 60 throttles the heating expansion valve 15a, throttles the cooling expansion valve 15b, fully closes the cooling expansion valve 15c, and fully closes the hot gas flow control valve 15d. The control device 60 also opens the dehumidification opening / closing valve 23a and the heating opening / closing valve 23b.

[0151] Therefore, in the heat pump cycle 10 in the single parallel dehumidification heating mode, the refrigerant discharged from the compressor 11 circulates in the order of the muffler section 12, the indoor condenser 14, the heating expansion valve 15a in the throttling state, the outdoor heat exchanger 16, the heating passage 22c, the accumulator section 21, and the suction port of the compressor 11. At the same time, the refrigerant discharged from the compressor 11 is switched to a refrigerant circuit in which the refrigerant circulates in the order of the muffler section 12, the indoor condenser 14, the dehumidification passage 22b, the cooling expansion valve 15b in the throttling state, the indoor evaporator 18, the evaporation pressure control valve 19, the accumulator section 21, and the suction port of the compressor 11. In other words, the outdoor heat exchanger 16 and the indoor evaporator 18 are switched to a refrigerant circuit in which the refrigerant flows in parallel.

[0152] In the indoor air conditioning unit 50 in the single parallel dehumidifying and heating mode, the opening degree of the air mix door 54, the inside / outside air switching device 53, and the operation of the blowing mode door are controlled in the same manner as in the single cooling mode. In addition, the control device 60 appropriately controls the operation of other control target devices.

[0153] Therefore, in the heat pump cycle 10 in the single-parallel dehumidifying and heating mode, a vapor compression refrigeration cycle is configured in which the indoor condenser 14 functions as a condenser, and the outdoor heat exchanger 16 and the indoor evaporator 18 function as evaporators.

[0154] In the interior air conditioning unit 50 in the single parallel dehumidifying and heating mode, the blown air blown from the interior blower 52 is cooled and dehumidified in the interior evaporator 18. The blown air cooled and dehumidified in the interior evaporator 18 is reheated in the interior condenser 14 so as to approach the target blown air temperature TAO according to the opening degree of the air mix door 54. Then, the temperature-adjusted blown air is blown into the vehicle cabin, thereby realizing dehumidifying and heating the vehicle cabin.

[0155] Furthermore, in the heat pump cycle 10 in the single-parallel dehumidifying and heating mode, the aperture of the heating expansion valve 15a can be made smaller than the aperture of the cooling expansion valve 15b. This allows the refrigerant evaporation temperature in the outdoor heat exchanger 16 to be lowered to a temperature lower than the refrigerant evaporation temperature in the indoor evaporator 18.

[0156] Therefore, in the single parallel dehumidifying and heating mode, the amount of heat absorbed by the refrigerant from the outside air in the outdoor heat exchanger 16 can be increased more than in the single series dehumidifying and heating mode, and the amount of heat dissipated from the refrigerant to the blown air in the indoor condenser 14 can be increased. As a result, in the single parallel dehumidifying and heating mode, the heating capacity of the blown air in the indoor condenser 14 can be improved more than in the single series dehumidifying and heating mode.

[0157] (c-2) Parallel cooling, dehumidification and heating mode In the heat pump cycle 10 in the cooling-parallel dehumidification-heating mode, the control device 60 controls the cooling expansion valve 15c to the throttling state, unlike in the single-parallel dehumidification-heating mode.

[0158] Therefore, in the heat pump cycle 10 in the cooling-parallel dehumidification-heating mode, the refrigerant discharged from the compressor 11 circulates in the same manner as in the single-parallel dehumidification-heating mode. At the same time, the refrigerant discharged from the compressor 11 is switched to a refrigerant circuit in which it circulates through the muffler section 12, the indoor condenser 14, the dehumidification passage 22b, the cooling expansion valve 15c in the throttling state, the chiller 20, the accumulator section 21, and the suction port of the compressor 11 in that order. In other words, the refrigerant circuit is switched to one in which the outdoor heat exchanger 16, the indoor evaporator 18, and the chiller 20 are connected in parallel with respect to the flow of the refrigerant.

[0159] In the cooling parallel dehumidification heating mode, the operation of the low-temperature side pump 31 is controlled in the same manner as in the cooling cooling mode. Therefore, in the low-temperature side heat medium circuit 30 in the cooling series dehumidification heating mode, the low-temperature side heat medium circulates in the same manner as in the cooling cooling mode.

[0160] In the indoor air conditioning unit 50 in the cooling parallel dehumidification heating mode, the opening degree of the air mix door 54, the inside / outside air switching device 53, and the operation of the blowing mode door are controlled in the same manner as in the single cooling mode. In addition, the control device 60 appropriately controls the operation of other control target devices.

[0161] Therefore, in the heat pump cycle 10 in the cooling parallel dehumidification heating mode, a vapor compression refrigeration cycle is configured in which the indoor condenser 14 functions as a condenser, and the outdoor heat exchanger 16, the indoor evaporator 18 and the chiller 20 function as evaporators.

[0162] In the low-temperature side heat medium circuit 30 in the cooling parallel dehumidification heating mode, the low-temperature side heat medium cooled in the chiller 20 flows through the coolant passage 80a of the battery 80, thereby cooling the battery 80, as in the cooling and air-conditioning mode.

[0163] In the interior air conditioning unit 50 in the cooling-parallel dehumidifying-heating mode, temperature-adjusted ventilation air is blown into the vehicle compartment, as in the single-parallel dehumidifying-heating mode, thereby realizing dehumidifying and heating the vehicle compartment.

[0164] (d) Heating mode The heating mode is an operation mode in which heated air is blown into the vehicle cabin to heat the vehicle cabin. In the control program of this embodiment, the operation mode for heating the vehicle cabin is executed mainly when the outside air temperature Tam is relatively low, such as in winter.

[0165] The heating mode includes a single heating mode in which the vehicle interior is heated without cooling the battery 80, and a cooling and heating mode in which the battery 80 is cooled and the vehicle interior is heated.

[0166] (d-1) Standalone heating mode In the heat pump cycle 10 in the single heating mode, the controller 60 throttles the heating expansion valve 15a, fully closes the cooling expansion valve 15b, fully closes the cooling expansion valve 15c, and fully closes the hot gas flow control valve 15d. The controller 60 also closes the dehumidification opening / closing valve 23a and opens the heating opening / closing valve 23b.

[0167] For this reason, in the heat pump cycle 10 in the sole heating mode, the refrigerant discharged from the compressor 11 is switched to a refrigerant circuit in which the refrigerant circulates in the following order: the muffler section 12, the indoor condenser 14, the heating expansion valve 15a which is in a throttling state, the outdoor heat exchanger 16, the heating passage 22c, the accumulator section 21, and the suction port of the compressor 11.

[0168] In the indoor air conditioning unit 50 in the single heating mode, the opening degree of the air mix door 54, the inside / outside air switching device 53, and the operation of the blowing mode door are controlled in the same manner as in the single cooling mode. In addition, the control device 60 appropriately controls the operation of other control target devices.

[0169] Therefore, in the heat pump cycle 10 in the sole heating mode, a vapor compression refrigeration cycle is configured in which the indoor condenser 14 functions as a condenser and the outdoor heat exchanger 16 functions as an evaporator.

[0170] In the interior air conditioning unit 50 in the single heating mode, the blown air sent from the interior blower 52 passes through the interior evaporator 18. The blown air that has passed through the interior evaporator 18 is reheated in the interior condenser 14 so as to approach the target blown air temperature TAO according to the opening degree of the air mix door 54. Then, the temperature-adjusted blown air is blown into the vehicle cabin, thereby heating the vehicle cabin.

[0171] (d-2) Cooling and heating mode In the heat pump cycle 10 in the cooling and heating mode, the controller 60 throttles the cooling expansion valve 15c in comparison with the single heating mode, and opens the dehumidification opening / closing valve 23a.

[0172] Therefore, in the heat pump cycle 10 in the cooling and heating mode, the refrigerant discharged from the compressor 11 circulates in the same manner as in the single heating mode. At the same time, the refrigerant discharged from the compressor 11 is switched to a refrigerant circuit in which it circulates through the muffler section 12, the indoor condenser 14, the dehumidification passage 22b, the cooling expansion valve 15c in the throttled state, the chiller 20, the accumulator section 21, and the suction port of the compressor 11 in that order. In other words, the refrigerant circuit is switched to one in which the outdoor heat exchanger 16 and the chiller 20 are connected in parallel with respect to the flow of the refrigerant.

[0173] In the cooling parallel dehumidification heating mode, the operation of the low-temperature side pump 31 is controlled in the same manner as in the cooling cooling mode. Therefore, in the low-temperature side heat medium circuit 30 in the cooling series dehumidification heating mode, the low-temperature side heat medium circulates in the same manner as in the cooling cooling mode.

[0174] In the indoor air conditioning unit 50 in the cooling parallel dehumidification heating mode, the opening degree of the air mix door 54, the inside / outside air switching device 53, and the operation of the blowing mode door are controlled in the same manner as in the single cooling mode. In addition, the control device 60 appropriately controls the operation of other control target devices.

[0175] Therefore, in the heat pump cycle 10 in the cooling / heating mode, a vapor compression refrigeration cycle is configured in which the indoor condenser 14 functions as a condenser, and the outdoor heat exchanger 16 and the chiller 20 function as evaporators.

[0176] In the low-temperature side heat medium circuit 30 in the cooling / heating mode, the low-temperature side heat medium cooled in the chiller 20 flows through the coolant passage 80a of the battery 80, as in the cooling / air-cooling mode, thereby cooling the battery 80.

[0177] In the interior air conditioning unit 50 in the cooling / heating mode, similarly to the single heating mode, temperature-adjusted ventilation air is blown into the vehicle compartment, thereby heating the vehicle compartment.

[0178] (e-1) Hot gas heating mode The hot gas heating mode is an operation mode that is executed to suppress a decrease in the heating capacity of the vehicle cabin when the outside air temperature Tam becomes extremely low (for example, −20° C. or lower).

[0179] In the hot gas heating mode, the controller 60 fully closes the heating expansion valve 15a, fully closes the cooling expansion valve 15b, throttles the cooling expansion valve 15c, and throttles the hot gas flow control valve 15d. The controller 60 also opens the dehumidification opening / closing valve 23a and closes the heating opening / closing valve 23b.

[0180] 5, in the heat pump cycle 10 in the hot gas heating mode, the refrigerant discharged from the compressor 11 circulates in the order of the muffler section 12, the indoor condenser 14, the dehumidification passage 22b, the cooling expansion valve 15c in the throttled state, the chiller 20, the accumulator section 21, and the suction port of the compressor 11. At the same time, the refrigerant discharged from the compressor 11 is switched to a refrigerant circuit in which the refrigerant circulates in the order of the muffler section 12, the hot gas flow control valve 15d in the hot gas passage 22a in the throttled state, the chiller 20, the accumulator section 21, and the suction port of the compressor 11.

[0181] In the hot gas heating mode, the low-temperature side pump 31 is stopped in the low-temperature side heat medium circuit 30. In the hot gas heating mode, the indoor air conditioning unit 50 controls the operation of the air mix door 54, the inside / outside air switching device 53, and the blowing mode door in the same manner as in the single cooling mode. The control device 60 also controls the operation of other control target devices as appropriate.

[0182] Therefore, in the heat pump cycle 10 in the hot gas heating mode, the flow of the refrigerant discharged from the compressor 11 is branched at the first inner three-way joint portion 13a.

[0183] One of the refrigerant branches at the first internal three-way joint 13a flows into the indoor condenser 14 and dissipates heat to the blown air. This heats the blown air. The refrigerant that flows out of the indoor condenser 14 flows through the dehumidification passage 22b into the cooling expansion valve 15c and is reduced in pressure. The refrigerant with a relatively low enthalpy that has been reduced in pressure by the cooling expansion valve 15c flows into the chiller 20 through the fourth internal three-way joint 13d.

[0184] On the other hand, the other refrigerant branched at the first internal three-way joint 13a is depressurized by adjusting the flow rate at the hot gas flow rate control valve 15d. The refrigerant with a relatively high enthalpy depressurized at the hot gas flow rate control valve 15d flows into the chiller 20 via the fourth internal three-way joint 13d.

[0185] In the chiller 20, the refrigerant decompressed by the cooling expansion valve 15c and the refrigerant decompressed by the hot gas flow rate control valve 15d are mixed. At this time, since the low-temperature side pump 31 is stopped, there is no heat exchange between the refrigerant and the low-temperature side heat medium in the chiller 20. The refrigerant flowing out of the chiller 20 flows into the accumulator section 21 and is separated into gas and liquid. The gas-phase refrigerant separated in the accumulator section 21 is sucked into the compressor 11 and compressed again.

[0186] In the interior air conditioning unit 50 in the hot gas heating mode, the ventilation air blown from the interior blower 52 passes through the interior evaporator 18. The ventilation air that has passed through the interior evaporator 18 is heated by the interior condenser 14 according to the opening degree of the air mix door 54. Then, the ventilation air heated by the interior condenser 14 is blown into the vehicle cabin, thereby heating the vehicle cabin.

[0187] More specifically, because the hot gas heating mode is an operation mode that is executed when the outdoor temperature is extremely low, if the refrigerant that flows out of the indoor condenser 14 is caused to flow into the outdoor heat exchanger 16, the refrigerant may lose heat to the outdoor air, causing a decrease in enthalpy of the refrigerant. Therefore, if the refrigerant that flows out of the indoor condenser 14 is caused to flow into the outdoor heat exchanger 16, the enthalpy of the refrigerant that flows into the chiller 20 is also likely to decrease.

[0188] Furthermore, if the refrigerant releases heat to the outside air in the outdoor heat exchanger 16, the amount of heat that the refrigerant releases to the blown air in the indoor condenser 14 decreases, which may result in a decrease in the heating capacity of the blown air.

[0189] On the other hand, in the hot gas heating mode, the refrigerant flowing out from the indoor condenser 14 is caused to flow into the cooling expansion valve 15c without flowing into the outdoor heat exchanger 16. Also, the low-temperature side pump 31 is stopped to prevent heat exchange between the refrigerant and the low-temperature side heat medium in the chiller 20. Furthermore, in the chiller 20, the refrigerant decompressed by the cooling expansion valve 15c and the refrigerant decompressed by the hot gas flow rate adjustment valve 15d are mixed.

[0190] Therefore, in the heat pump cycle 10 in the hot gas heating mode, even if the refrigerant discharge capacity of the compressor 11 is increased compared to the heating mode, the suction side refrigerant flowing out from the chiller 20 to the suction port side of the compressor 11 can be a gas phase refrigerant having a degree of superheat. In addition, by increasing the compression work load of the compressor 11, a decrease in the amount of heat dissipated from the refrigerant in the indoor condenser 14 to the blown air can be suppressed.

[0191] As a result, in the hot gas heating mode, it is possible to realize heating of the vehicle cabin while suppressing a decrease in the heating capacity of the blown air.

[0192] Here, the hot gas heating mode is an operation mode executed when the outside air temperature is extremely low, and therefore there is no need to cool the battery 80. In contrast, when the outside air temperature is low, it may be necessary to warm up the battery 80. Therefore, the vehicle air conditioner 1 of this embodiment can execute a warm-up hot gas heating mode for warming up the battery 80, which is an in-vehicle device.

[0193] More specifically, in the vehicle air conditioning device 1 of this embodiment, when the hot gas heating mode is being executed and the battery temperature TB detected by the battery temperature sensor 64 becomes equal to or lower than a predetermined reference lower limit temperature KTBL, the warm-up hot gas heating mode is executed.

[0194] (e-2) Warm-up hot gas heating mode In the low-temperature side heat medium circuit 30 in the warm-up hot gas heating mode, the control device 60 operates the low-temperature side pump 31 so as to exert a predetermined reference pumping capacity. Therefore, in the low-temperature side heat medium circuit 30, the low-temperature side heat medium pumped by the low-temperature side pump 31 circulates through the heat medium passage of the chiller 20 and then through the cooling water passage 80a of the battery 80. Other operations are the same as in the hot gas heating mode.

[0195] Therefore, in the heat pump cycle 10 in the warm-up hot gas heating mode, the refrigerant that flows into the chiller 20 releases heat to the low-temperature side heat medium. This heats the low-temperature side heat medium. In the low-temperature side heat medium circuit 30 in the warm-up hot gas heating mode, the low-temperature side heat medium heated by the chiller 20 flows through the coolant passage 80a of the battery 80. This warms up the battery 80.

[0196] (f) Single cooling mode The single cooling mode is an operation mode in which the battery 80 is cooled without air conditioning the interior of the vehicle.

[0197] In the heat pump cycle 10 in the single cooling mode, the control device 60 fully opens the heating expansion valve 15a, fully closes the cooling expansion valve 15b, throttles the cooling expansion valve 15c, and fully closes the hot gas flow control valve 15d. The control device 60 also closes the dehumidification opening / closing valve 23a and the heating opening / closing valve 23b.

[0198] For this reason, in the heat pump cycle 10 in the sole cooling mode, the refrigerant discharged from the compressor 11 is switched to a refrigerant circuit in which it circulates in the following order: the muffler section 12, the indoor condenser 14, the heating expansion valve 15a which is in a fully open state, the outdoor heat exchanger 16, the cooling expansion valve 15c which is in a throttled state, the chiller 20, the accumulator section 21, and the suction port of the compressor 11.

[0199] In the low-temperature side heat medium circuit 30 in the single cooling mode, the low-temperature side heat medium pumped from the low-temperature side pump 31 circulates in the same manner as in the cooling / air-conditioning mode. In the indoor air-conditioning unit 50 in the single cooling mode, the indoor blower 52 is stopped.

[0200] Therefore, in the heat pump cycle 10 in the single cooling mode, a vapor compression refrigeration cycle is configured in which the outdoor heat exchanger 16 functions as a condenser and the chiller 20 functions as an evaporator.

[0201] In the low-temperature side heat medium circuit 30 in the single cooling mode, the low-temperature side heat medium cooled in the chiller 20 flows through the coolant passage 80a of the battery 80, as in the cooling / air-cooling mode, thereby cooling the battery 80.

[0202] As described above, in the vehicle air conditioner 1 of this embodiment, by switching the operation mode, it is possible to perform comfortable air conditioning for the vehicle interior and appropriate temperature adjustment for the battery 80, which is an on-board device.

[0203] Furthermore, in this embodiment, since the compressor module 100 is employed, the noise of the compressor 11 can be sufficiently suppressed without causing a decrease in productivity of the vehicle air conditioner 1, which is a heat pump cycle device.

[0204] More specifically, in the compressor module 100, the refrigerant discharged from the compressor 11 can be made to flow through the internal refrigerant passage of the flow path box 101 to the external components such as the indoor condenser 14, the outdoor heat exchanger 16, and the indoor evaporator 18. Similarly, the refrigerant flowing out from the external components can be sucked into the compressor 11 through the internal refrigerant passage of the flow path box 101.

[0205] Therefore, there is no need to form a through hole or the like in the flow path box 101 or the cover member 102 for passing a pipe connecting the compressor 11 to an external component device. Therefore, noise from the compressor 11 does not leak out to the outside of the accommodation space 103 through a gap between the through hole and the pipe. Furthermore, there is no need to block the gap between the through hole and the pipe with a soundproof sealing member or the like.

[0206] As a result, noise can be sufficiently suppressed without deteriorating the productivity of the heat pump cycle apparatus 1. Furthermore, in the compressor module 100 of the present embodiment, the accommodation space 103 is formed as a sealed space, so that noise of the compressor 11 does not leak out to the outside of the accommodation space 103 through other gaps.

[0207] In addition, the low-pressure hose 11a and the high-pressure hose 11b of the compressor module 100 of this embodiment have flexible and elastically deformable refrigerant hose portions. The low-pressure hose 11a and the high-pressure hose 11b are attached to the compressor 11 and the flow path box 101 in a curved state.

[0208] This makes it possible to suppress the vibration of the compressor 11 from being transmitted to the flow path box 101 and the cover member 102 via the low pressure hose 11a and the high pressure hose 11b. Therefore, it is possible to suppress the generation of noise by the flow path box 101 and the cover member 102 due to the vibration transmitted from the compressor 11.

[0209] Moreover, in the compressor module 100 of this embodiment, a thermoplastic anti-vibration rubber 11c is disposed between the compressor 11 and the fixed portion 101s of the flow path box 101. Furthermore, the heat of the compressor 11 can be transferred to the anti-vibration rubber 11c to heat the anti-vibration rubber 11c.

[0210] According to this, even when the outside air temperature is low, the heat of the compressor 11 is transferred to the vibration-proof rubber 11c to heat the vibration-proof rubber 11c, thereby suppressing a decrease in the elasticity of the vibration-proof rubber 11c. Therefore, it is possible to effectively suppress the vibration of the compressor 11 from being transferred to the flow path box 101 and the cover member 102, which would otherwise cause the flow path box 101 and the cover member 102 to generate noise.

[0211] Moreover, the compressor module 100 of this embodiment is provided with a heat insulating material 104. This makes it possible to suppress unnecessary radiation of heat from within the accommodation space 103 through the outer surface of the compressor module 100 even when the outside air temperature is low. This is effective in a heat pump cycle device that needs to operate even when the outside air temperature is extremely low. Furthermore, the heat insulating material 104 can provide an even greater soundproofing effect.

[0212] In addition, in this embodiment, a heat insulating material 104 is disposed on the outer surface of the compressor module 100. Therefore, for example, by attaching a sheet-shaped heat insulating material to the outer surface of the compressor module 100, the heat insulating material 104 can be easily attached to the compressor module 100.

[0213] In addition, in the heat pump cycle device 1 of this embodiment, during hot gas heating mode, the refrigerant circuit of the heat pump cycle 10 is switched to a refrigerant circuit in which the refrigerant flowing out from the indoor condenser 14 and the other refrigerant branched at the first internal three-way joint portion 13a are merged and sucked into the compressor 11.

[0214] Since the hot gas heating mode is an operation mode executed when the outside air temperature is extremely low, the refrigerant discharge capacity (i.e., the rotation speed) of the compressor 11 is increased more than in the heating mode. This also tends to increase the noise of the compressor 11. Therefore, applying the compressor module 100 to a heat pump cycle device capable of executing the hot gas heating mode is extremely effective in suppressing noise.

[0215] Second embodiment In this embodiment, an example will be described in which a compressor module 110 according to the present invention is applied to a vehicle air conditioner 1a shown in the overall configuration diagram of Fig. 6. The vehicle air conditioner 1a is a heat pump cycle device that performs air conditioning in a vehicle cabin and temperature adjustment of on-board equipment, similar to the vehicle air conditioner 1 described in the first embodiment. Note that in Fig. 6, an interior air conditioning unit 50 is omitted for clarity of illustration.

[0216] The vehicle air conditioner 1a includes a high-temperature side heat medium circuit 40 in addition to a heat pump cycle 10a, a low-temperature side heat medium circuit 30a, an interior air conditioning unit 50, and the like.

[0217] In the heat pump cycle 10a of the present embodiment, compared to the heat pump cycle 10 described in the first embodiment, the muffler section 12, the indoor condenser 14, the heating expansion valve 15a, the outdoor heat exchanger 16, the dehumidification passage 22b, the heating passage 22c, the dehumidification on-off valve 23a, the heating on-off valve 23b, etc. are eliminated.

[0218] The compressor module 110 is a component that integrates a plurality of components that mainly configure the heat pump cycle 10a. In the compressor module 110 of the present embodiment, the components surrounded by the dashed line in FIG. 6 are integrated.

[0219] More specifically, in the compressor module 110 of this embodiment, among the components of the heat pump cycle 10a, the compressor 11, the water-refrigerant heat exchanger 141, the cooling expansion valve 15b, the cooling expansion valve 15c, the hot gas flow control valve 15d, the evaporation pressure control valve 19, the chiller 20, etc. are integrated.

[0220] These components are integrated by being attached to a flow path box 111 of the compressor module 110. Also, the receiver section 141b of the water-refrigerant heat exchanger 141 is integrally formed in the flow path box 111. The flow path box 111 is an attachment member and a passage forming member similar to the flow path box 101 described in the first embodiment.

[0221] As in the first embodiment, a compressor-side inlet 111b formed in a flow path box 111 is connected to a discharge port of the compressor 11 of the heat pump cycle 10a via a high-pressure hose 11b. The compressor-side inlet 111b is connected to an inlet of the first internal three-way joint portion 13a via an internal refrigerant passage.

[0222] One of the outlets of the first internal three-way joint 13a is connected through an internal refrigerant passage to a condenser-side outlet 111c formed in the flow path box 111. The other of the outlets of the first internal three-way joint 13a is connected through a hot gas passage 22a to one of the inlets of a fourth internal three-way joint 13d. As in the first embodiment, a hot gas flow rate control valve 15d is disposed in the hot gas passage 22a.

[0223] The condenser side outlet 111c is directly connected to an inlet of a refrigerant passage of the water-refrigerant heat exchanger 141. More specifically, the inlet of a condensing section 141a of the water-refrigerant heat exchanger 141 is directly connected to the condenser side outlet 111c. The water-refrigerant heat exchanger 141 is a heat exchange section that exchanges heat between the refrigerant discharged from the compressor 11 and the high-temperature side heat medium circulating in the high-temperature side heat medium circuit 40.

[0224] In the heat pump cycle 10a, a so-called subcooling type heat exchanger is adopted as the water-refrigerant heat exchanger 141. Therefore, the water-refrigerant heat exchanger 141 has a condenser section 141a, a receiver section 141b, and a subcooling section 141c.

[0225] The condensation section 141a is a heat exchange section for condensation that exchanges heat between the refrigerant discharged from the compressor 11 and a high-pressure side heat medium to condense the high-pressure side refrigerant. An inlet of a receiver section 141b formed in the flow path box 111 is connected to a refrigerant outlet of the condensation section 141a.

[0226] The receiver 141b is a high-pressure side gas-liquid separator that separates the refrigerant flowing out from the condenser 141a into gas and liquid and stores the separated liquid-phase refrigerant as surplus refrigerant for the cycle. The outlet of the receiver 141b formed in the flow path box 111 is connected to the refrigerant inlet of the supercooling unit 141c.

[0227] The supercooling section 141c is a heat exchange section for supercooling the liquid-phase refrigerant by exchanging heat between the liquid-phase refrigerant flowing out from the receiver section 141b and the high-pressure side heat medium. Therefore, the water-refrigerant heat exchanger 141 including the receiver section 141b is a high-pressure side refrigerant device.

[0228] A condenser-side inlet 111d formed in the flow path box 111 is directly connected to an outlet of the subcooling section 141c of the water-refrigerant heat exchanger 141. The condenser-side inlet 111d is connected to an inlet of the seventh internal three-way joint 13g via an internal refrigerant passage.

[0229] One of the outlets of the seventh internal three-way joint portion 13g is connected through an internal refrigerant passage to an evaporator side outlet 111g formed in the flow path box 111. A cooling expansion valve 15b is disposed in the internal refrigerant passage extending from one of the outlets of the seventh internal three-way joint portion 13g to the evaporator side outlet 111g.

[0230] The evaporator-side outlet 111g is connected to a refrigerant inlet side of the indoor evaporator 18. The refrigerant outlet of the indoor evaporator 18 is connected to an evaporator-side inlet 111h formed in the flow path box 111.

[0231] The other outlet of the seventh internal three-way joint 13g is connected to the other inlet of the fourth internal three-way joint 13d via an internal refrigerant passage. A cooling expansion valve 15c is disposed in the internal refrigerant passage extending from the other outlet of the seventh internal three-way joint 13g to the other inlet of the fourth internal three-way joint 13d.

[0232] An outlet of the fourth internal three-way joint portion 13d is connected to a chiller-side outlet 111i formed in the flow path box 111. A refrigerant inlet of the chiller 20 is directly connected to the chiller-side outlet 111i. A refrigerant outlet of the chiller 20 is directly connected to a chiller-side inlet 111j formed in the flow path box 111. The rest of the configuration of the heat pump cycle 10a is similar to that of the heat pump cycle 10 described in the first embodiment.

[0233] Next, a detailed configuration of the compressor module 110 will be described with reference to Fig. 7. The basic configuration of the compressor module 110 is similar to that of the compressor module 100 described in the first embodiment. The compressor module 110 includes a metal flow path box 111. The compressor module 110 also includes a resin cover member (not shown).

[0234] As in the first embodiment, the cover member is attached to the flow path box 111 to form an accommodation space 113, which is an enclosed space for accommodating the compressor 11 and the like, inside the compressor module 110. The appearance of the compressor module 110 is also a rectangular parallelepiped shape, as in the first embodiment. Furthermore, a heat insulating material (not shown) is arranged on the outer surface of the compressor module 110, as in the first embodiment.

[0235] In addition to the compressor 11, the accommodation space 113 accommodates a water-refrigerant heat exchanger 141, a cooling expansion valve 15b, a cooling expansion valve 15c, a hot gas flow rate control valve 15d, an evaporation pressure control valve 19, and a chiller 20.

[0236] For this reason, the compressor side outlet 111a, the compressor side inlet 111b, the condenser side outlet 111c, the condenser side inlet 111d, the chiller side outlet 111i, and the chiller side inlet 111j are formed inside the accommodation space 113. More specifically, the compressor side outlet 111a and the compressor side inlet 111b are formed on the inner surface of the flow path box 111 on the accommodation space 113 side, and are thereby formed inside the accommodation space 113.

[0237] Moreover, the indoor evaporator 18 is disposed outside the accommodation space 113. Therefore, the indoor evaporator 18 in this embodiment is an external component device. The evaporator side outlet 111g and the evaporator side inlet 111h are formed on the outer surface on the outer periphery side of the flow path box 111, and are thereby formed outside the accommodation space 113. Therefore, the evaporator side outlet 111g and the evaporator side inlet 111h in this embodiment are external connection ports.

[0238] In addition, as in the first embodiment, the compressor 11 is fixed to multiple (four in this embodiment) fixing portions 111s formed on the bottom surface that forms the storage space 113 of the flow path box 111 via vibration-proof rubber 11c.

[0239] In addition, the water-refrigerant heat exchanger 141 is fixed to the flow path box 111 by fitting the refrigerant inlet / outlet and the heat medium inlet / outlet formed to protrude to the outside into the refrigerant inlet / outlet (i.e., the condenser side outlet 111c, the condenser side inlet 111d, etc.) and the heat medium inlet / outlet formed in the flow path box 111, respectively.

[0240] Moreover, the receiver portion 141b is formed in a shape that bulges toward the accommodation space 113 in order to form a liquid storage space. The receiver portion 141b is disposed on the bottom surface of the flow path box 111 so as to be surrounded by a plurality of fixing portions 111s. In other words, the plurality of fixing portions 111s are disposed around the portion where the receiver portion 141b is formed.

[0241] As a result, in the compressor module 110, the heat of the high-pressure side refrigerant in the receiver section 141b is transferred to the vibration-proof rubber 11c, so that the vibration-proof rubber 11c can be heated. In other words, the vibration-proof rubber 11c is arranged so that it can be heated by the heat of the high-pressure side refrigerant in the receiver section 141b. The fixing and electrical connections of the other components are the same as those in the first embodiment.

[0242] Next, the low-temperature side heat medium circuit 30a will be described. The low-temperature side heat medium circuit 30a is configured to be able to switch the heat medium circuit according to various operation modes described later. As shown in Fig. 6, the low-temperature side pump 31, the low-temperature side flow rate control valve 32, the low-temperature side radiator 34, the cooling water passage 80a of the battery 80, the heat medium passage of the chiller 20 of the compressor module 110, etc. are connected to the low-temperature side heat medium circuit 30a.

[0243] The low-temperature side pump 31 of this embodiment pumps the low-temperature side heat medium flowing out from the low-temperature side three-way joint 33 to a low-temperature side heat medium inlet 111m formed in the flow path box 111 of the compressor module 110. The low-temperature side three-way joint 33 is a three-way joint for the low-temperature side heat medium having three inlet and outlets that communicate with each other.

[0244] The low-temperature side heat medium inlet 111m communicates with an inlet of a heat medium passage of the chiller 20 via an internal heat medium passage. The outlet of the heat medium passage of the chiller 20 communicates with a low-temperature side heat medium outlet 111n formed in the flow path box 111 via an internal heat medium passage.

[0245] The low-temperature side heat medium outlet 111n is connected to an inlet of the low-temperature side flow rate adjustment valve 32. One outlet of the low-temperature side flow rate adjustment valve 32 is connected to an inlet side of a cooling water passage 80a of the battery 80. The other outlet of the low-temperature side flow rate adjustment valve 32 is connected to the heat medium inlet side of the low-temperature side radiator 34.

[0246] The low-temperature side flow rate adjustment valve 32 is a three-way low-temperature side heat medium flow rate adjustment unit that can continuously adjust the flow rate ratio between the flow rate of the low-temperature side heat medium flowing out from the low-temperature side heat medium outlet 111n that is caused to flow out to the coolant passage 80a of the battery 80 and the flow rate of the low-temperature side heat medium that is caused to flow out to the low-temperature side radiator 34. The operation of the low-temperature side flow rate adjustment valve 32 is controlled by a control signal output from the control device 60. The low-temperature side flow rate adjustment valve 32 is included in the electric device.

[0247] The low-temperature side flow rate adjustment valve 32 adjusts the flow rate ratio to allow the low-temperature side heat medium to flow only to either the coolant passage 80a of the battery 80 or the low-temperature side radiator 34. Therefore, the low-temperature side flow rate adjustment valve 32 is a low-temperature side heat medium circuit switching unit that switches the circuit configuration of the low-temperature side heat medium circuit 30a.

[0248] The low-temperature side radiator 34 is a heat exchanger that exchanges heat between the low-temperature side heat medium and the outside air. The low-temperature side radiator 34 is disposed in the drive unit room together with a high-temperature side radiator 44, which will be described later. One of the inlets of the low-temperature side three-way joint 33 is connected to a heat medium outlet of the low-temperature side radiator 34. The other inlet of the low-temperature side three-way joint 33 is connected to an outlet of the cooling water passage 80a of the battery 80.

[0249] Next, the high-temperature side heat medium circuit 40 will be described. The high-temperature side heat medium circuit 40 is a heat medium circuit that circulates the high-temperature side heat medium. In the high-temperature side heat medium circuit 40, the same type of fluid as the low-temperature side heat medium is used as the high-temperature side heat medium. The high-temperature side heat medium circuit 40 is configured to be able to switch the heat medium circuit according to various operation modes described later.

[0250] As shown in FIG. 6, the high-temperature side heat medium circuit 40 is connected to a high-temperature side pump 41, a high-temperature side flow control valve 42, a high-temperature side radiator 44, a heater core 45, and a heat medium passage of a water-refrigerant heat exchanger 141 of the compressor module 110.

[0251] The high-temperature side pump 41 is a high-temperature side heat medium pumping section that sucks in and pumps the high-temperature side heat medium. The high-temperature side pump 41 pumps the high-temperature side heat medium flowing out from the outlet of the high-temperature side three-way joint section 43 to the high-temperature side heat medium inlet 111p formed in the flow path box 111 of the compressor module 110. The basic configuration of the high-temperature side pump 41 is the same as that of the low-temperature side pump 31. The basic configuration of the high-temperature side three-way joint section 43 is the same as that of the low-temperature side three-way joint section 33.

[0252] The high temperature side heat medium inlet 111p is connected via an internal heat medium passage to an inlet of a heat medium passage of the water-refrigerant heat exchanger 141. The outlet of the heat medium passage of the water-refrigerant heat exchanger 141 is connected to a high temperature side heat medium outlet 111q formed in the flow path box 111 via an internal heat medium passage.

[0253] The high-temperature side heat medium outlet 111q is connected to the inlet of the high-temperature side flow rate control valve 42. The heat medium inlet side of the high-temperature side radiator 44 is connected to one outlet of the high-temperature side flow rate control valve 42. The heat medium inlet side of the heater core 45 is connected to the other outlet of the high-temperature side flow rate control valve 42.

[0254] The high-temperature side flow rate control valve 42 is a three-way high-temperature side heat medium flow rate control unit that can continuously adjust the flow rate ratio between the flow rate of the high-temperature side heat medium flowing out from the high-temperature side heat medium outlet 111q that flows out to the high-temperature side radiator 44 side and the flow rate of the high-temperature side heat medium flowing out to the heater core 45 side. The high-temperature side flow rate control valve 42 has a basic configuration similar to that of the low-temperature side flow rate control valve 32.

[0255] The high-temperature side flow rate adjustment valve 42 adjusts the flow rate ratio to allow the high-temperature side heat medium to flow to only one of the high-temperature side radiator 44 and the heater core 45. Therefore, the high-temperature side flow rate adjustment valve 42 is a high-temperature side heat medium circuit switching unit that switches the circuit configuration of the high-temperature side heat medium circuit 40.

[0256] The high-temperature side radiator 44 is a heat exchanger that exchanges heat between the high-temperature side heat medium and the outside air. The high-temperature side radiator 44 is disposed in the drive device compartment together with the low-temperature side radiator 34. The high-temperature side radiator 44 is disposed upstream of the low-temperature side radiator 34 in the flow of outside air in the drive device compartment. Therefore, the low-temperature side radiator 34 exchanges heat between the low-temperature side heat medium and the outside air that has passed through the high-temperature side radiator 44.

[0257] The heater core 45 is disposed in the air conditioning case 51 of the indoor air conditioning unit 50 in the same manner as the indoor condenser 14 described in the first embodiment. The heater core 45 is a heat exchanger that exchanges heat between the high-temperature side heat medium heated in the water-refrigerant heat exchanger 141 and the blown air. The heater core 45 releases heat from the high-temperature side heat medium to the blown air, heating the blown air.

[0258] Therefore, in the high-temperature side heat medium circuit 40, the high-temperature side heat medium can be heated by heat exchange between the high-pressure side refrigerant and the high-temperature side heat medium in the water-refrigerant heat exchanger 141. Furthermore, the high-temperature side heat medium and the blown air can be heat exchanged in the heater core 45, so that the blown air can be heated. Therefore, in this embodiment, the water-refrigerant heat exchanger 141 and each component of the high-temperature side heat medium circuit 40 serve as a heating section that heats the air using the refrigerant discharged from the compressor 11 as a heat source.

[0259] In addition, a high-temperature side heat medium temperature sensor 63b is connected to the input side of the control device 60 of this embodiment. The high-temperature side heat medium temperature sensor 63b is a high-temperature side heat medium temperature detection unit that detects a high-temperature side heat medium temperature TWH, which is the temperature of the high-temperature side heat medium flowing into the heater core 45.

[0260] Other configurations of the vehicle air conditioner 1a are similar to those of the vehicle air conditioner 1 described in the first embodiment.

[0261] Next, the operation of the vehicle air conditioner 1a of this embodiment with the above configuration will be described. In the vehicle air conditioner 1a, similar to the vehicle air conditioner 1 described in the first embodiment, various operation modes are switched to perform air conditioning in the vehicle cabin and temperature adjustment of the battery 80. The detailed operation of each operation mode will be described below.

[0262] (a-1) Single cooling mode In the heat pump cycle 10a in the single cooling mode, the controller 60 controls the cooling expansion valve 15b to be in a throttled state, the cooling expansion valve 15c to be in a fully closed state, and the hot gas flow rate adjustment valve 15d to be in a fully closed state.

[0263] Therefore, in the heat pump cycle 10a in the cooling only mode, the refrigerant discharged from the compressor 11 is switched to a refrigerant circuit in which it circulates in the following order: the water-refrigerant heat exchanger 141, the cooling expansion valve 15b in the throttling state, the indoor evaporator 18, the evaporation pressure control valve 19, and the suction port of the compressor 11.

[0264] In the high-temperature side heat medium circuit 40 in the single cooling mode, the high-temperature side pump 41 is operated to exert a predetermined reference pumping capacity. Furthermore, the operation of the high-temperature side flow rate control valve 42 is controlled so that the high-temperature side heat medium temperature TWH approaches a predetermined reference high-temperature side heat medium temperature KTWH.

[0265] For this reason, in the high-temperature side heat medium circuit 40 in the single cooling mode, the low-temperature side heat medium pumped by the high-temperature side pump 41 circulates in this order: water-refrigerant heat exchanger 141, heater core 45, and the suction port of the high-temperature side pump 41. At the same time, the circuit configuration is switched to one in which the low-temperature side heat medium pumped by the high-temperature side pump 41 circulates in this order: water-refrigerant heat exchanger 141, high-temperature side radiator 44, and the suction port of the high-temperature side pump 41.

[0266] Here, in the cooling mode for cooling the vehicle interior, the amount of heat dissipated from the high-temperature side heat medium to the blown air is reduced in the heater core 45. For this reason, in the cooling mode, the high-temperature side flow rate adjustment valve 42 often causes almost the entire flow rate of the high-temperature side heat medium flowing out from the high-temperature side heat medium outlet 111q to flow to the high-temperature side radiator 44 side.

[0267] In the indoor air conditioning unit 50 in the single cooling mode, the opening degree of the air mix door 54 is controlled so that the blowing air temperature TAV approaches the target blowing temperature TAO, as in the single cooling mode of the first embodiment. In the indoor air conditioning unit 50 in the single cooling mode, the operation of the inside / outside air switching device 53 and the blowing mode door is controlled based on the target blowing temperature TAO. The control device 60 also controls the operation of other control target devices as appropriate.

[0268] Therefore, in the heat pump cycle 10a in the single cooling mode, a vapor compression refrigeration cycle is configured in which the water-refrigerant heat exchanger 141 functions as a condenser and the indoor evaporator 18 functions as an evaporator.

[0269] In the high-temperature side heat medium circuit 40 in the sole cooling mode, the high-temperature side heat medium pumped from the high-temperature side pump 41 is heated in the water-refrigerant heat exchanger 141. The high-temperature side heat medium heated in the water-refrigerant heat exchanger 141 flows into the high-temperature side radiator 44 and the heater core 45 in response to the operation of the high-temperature side flow control valve 42. The high-temperature side heat medium that flows into the high-temperature side radiator 44 is cooled by dissipating heat to the outside air. The high-temperature side heat medium that flows into the heater core 45 dissipates heat to the blown air.

[0270] In the interior air conditioning unit 50 in the single cooling mode, the blown air blown from the interior blower 52 is cooled by the interior evaporator 18. The blown air cooled by the interior evaporator 18 is reheated by the heater core 45 so as to approach the target blown air temperature TAO according to the opening degree of the air mix door 54. Then, the temperature-adjusted blown air is blown into the vehicle cabin, thereby cooling the vehicle cabin.

[0271] (a-2) Cooling mode In the heat pump cycle 10a in the cooling / air-cooling mode, the controller 60 controls the cooling expansion valve 15c to be in the throttling state in contrast to the single cooling mode.

[0272] Therefore, in the heat pump cycle 10a in the cooling / cooling mode, the refrigerant discharged from the compressor 11 circulates in the order of the water-refrigerant heat exchanger 141, the cooling expansion valve 15b in the throttled state, the indoor evaporator 18, the evaporation pressure regulating valve 19, 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 water-refrigerant heat exchanger 141, the cooling expansion valve 15c in the throttled state, the chiller 20, and the suction port of the compressor 11. In other words, the indoor evaporator 18 and the chiller 20 are switched to a refrigerant circuit connected in parallel with respect to the flow of the refrigerant.

[0273] In the low-temperature side heat medium circuit 30a in the cooling / air-cooling mode, the controller 60 operates the low-temperature side pump 31 to achieve a predetermined reference pumping capacity. Furthermore, the controller 60 controls the operation of the low-temperature side flow rate adjustment valve 32 to cause the entire flow rate of the high-temperature side heat medium flowing out from the low-temperature side heat medium outlet 111n to flow to the cooling water passage 80a of the battery 80.

[0274] Therefore, in the low-temperature side heat medium circuit 30a in the cooling / air-conditioning mode, the circuit configuration is switched to one in which the low-temperature side heat medium pumped by the low-temperature side pump 31 circulates through the chiller 20, the cooling water passage 80a of the battery 80, and the suction port of the low-temperature side pump 31 in that order.

[0275] In the high-temperature side heat medium circuit 40 in the cooling / cooling mode, the operation of the high-temperature side pump 41 and the high-temperature side flow rate adjustment valve 42 are controlled in the same manner as in the single cooling mode.

[0276] In the indoor air conditioning unit 50 in the cooling / cooling mode, the opening degree of the air mix door 54, the inside / outside air switching device 53, and the operation of the blowing mode door are controlled in the same manner as in the single cooling mode. In addition, the control device 60 appropriately controls the operation of other control target devices.

[0277] Therefore, in the heat pump cycle 10a in the cooling / air-conditioning mode, the water-refrigerant heat exchanger 141 functions as a condenser that dissipates heat from the refrigerant to condense it, and the indoor evaporator 18 and the chiller 20 function as evaporators that evaporate the refrigerant, forming a vapor compression refrigeration cycle.

[0278] In the low-temperature side heat medium circuit 30a in the cooling / air-cooling mode, the low-temperature side heat medium pumped from the low-temperature side pump 31 flows into the chiller 20 and is cooled. Then, the low-temperature side heat medium cooled in the chiller 20 flows through the coolant passage 80a of the battery 80, thereby cooling the battery 80.

[0279] In the high-temperature side heat medium circuit 40 in the cooling / air-cooling mode, the high-temperature side heat medium that flows into the high-temperature side radiator 44 is cooled by dissipating heat to the outside air, as in the single cooling mode. The high-temperature side heat medium that flows into the heater core 45 dissipates heat to the blown air.

[0280] In the interior air conditioning unit 50 in the cooling / air-conditioning mode, temperature-adjusted air is blown into the vehicle compartment, thereby cooling the vehicle compartment, similarly to the single cooling mode.

[0281] (b-1) Single dehumidification and heating mode In the heat pump cycle 10a in the single dehumidification heating mode, the controller 60 throttles the cooling expansion valve 15b, throttles the cooling expansion valve 15c, and fully closes the hot gas flow rate control valve 15d.

[0282] Therefore, in the heat pump cycle 10a in the single dehumidification heating mode, the refrigerant circuit is switched in the same manner as in the cooling / cooling mode. That is, the refrigerant circuit is switched to one in which the indoor evaporator 18 and the chiller 20 are connected in parallel with respect to the flow of the refrigerant.

[0283] In the low-temperature side heat medium circuit 30a in the single dehumidification and heating mode, the controller 60 operates the low-temperature side pump 31 to exert a predetermined reference pumping capacity. Furthermore, the controller 60 controls the operation of the low-temperature side flow rate adjustment valve 32 to cause the entire flow rate of the high-temperature side heat medium flowing out from the low-temperature side heat medium outlet 111n to flow to the low-temperature side radiator 34 side.

[0284] For this reason, in the low-temperature side heat medium circuit 30a in the single dehumidification heating mode, the circuit configuration is switched to one in which the low-temperature side heat medium pumped by the low-temperature side pump 31 circulates through the chiller 20, the low-temperature side radiator 34, and the suction port of the low-temperature side pump 31 in that order.

[0285] In the high-temperature side heat medium circuit 40 in the single dehumidification and heating mode, the operations of the high-temperature side pump 41 and the high-temperature side flow rate adjustment valve 42 are controlled in the same manner as in the single cooling mode.

[0286] In the indoor air conditioning unit 50 in the single dehumidification heating mode, the opening degree of the air mix door 54, the inside / outside air switching device 53, and the operation of the blowing mode door are controlled in the same manner as in the single cooling mode. In addition, the control device 60 appropriately controls the operation of other control target devices.

[0287] Therefore, in the heat pump cycle 10a in the single dehumidification heating mode, a vapor compression refrigeration cycle is configured in which the water-refrigerant heat exchanger 141 functions as a condenser, and the indoor evaporator 18 and the chiller 20 function as evaporators.

[0288] In the low-temperature side heat medium circuit 30a in the single dehumidification and heating mode, the low-temperature side heat medium pumped from the low-temperature side pump 31 flows into the chiller 20 and is cooled. The low-temperature side heat medium cooled in the chiller 20 flows into the low-temperature side radiator 34. In the low-temperature side radiator 34, the low-temperature side heat medium exchanges heat with the outside air and absorbs heat from the outside air.

[0289] In the high-temperature side heat medium circuit 40 in the single dehumidification and heating mode, the high-temperature side heat medium that flows into the high-temperature side radiator 44 is cooled by dissipating heat to the outside air, as in the single cooling mode. The high-temperature side heat medium that flows into the heater core 45 dissipates heat to the blown air.

[0290] In the interior air conditioning unit 50 in the single dehumidification heating mode, the blown air blown from the interior blower 52 is cooled and dehumidified by the interior evaporator 18. The blown air cooled and dehumidified by the interior evaporator 18 is reheated by the heater core 45 so as to approach the target blown air temperature TAO according to the opening degree of the air mix door 54. Then, the temperature-adjusted blown air is blown into the vehicle cabin, thereby realizing dehumidification and heating of the vehicle cabin.

[0291] (b-2) Cooling, dehumidifying and heating mode In the heat pump cycle 10a in the cooling / dehumidifying / heating mode, as in the single dehumidifying / heating mode, the control device 60 throttles the cooling expansion valve 15b, throttles the cooling expansion valve 15c, and fully closes the hot gas flow control valve 15d.

[0292] Therefore, in the heat pump cycle 10a in the cooling / dehumidifying / heating mode, the refrigerant circuit is switched in the same manner as in the single dehumidifying / heating mode. That is, the refrigerant circuit is switched to one in which the indoor evaporator 18 and the chiller 20 are connected in parallel with respect to the flow of the refrigerant.

[0293] In the low-temperature side heat medium circuit 30a in the cooling / dehumidifying / heating mode, the controller 60 operates the low-temperature side pump 31 to exert a predetermined reference pumping capacity. Furthermore, in the low-temperature side heat medium circuit 30a, the operation of the low-temperature side flow rate control valve 32 is controlled so that the low-temperature side heat medium temperature TWL detected by the low-temperature side heat medium temperature sensor 63a approaches a predetermined reference low-temperature side heat medium temperature KTWL.

[0294] In the high-temperature side heat medium circuit 40 in the cooling / dehumidifying / heating mode, the operation of the high-temperature side pump 41 and the high-temperature side flow rate adjustment valve 42 are controlled in the same manner as in the single cooling mode.

[0295] In the indoor air conditioning unit 50 in the cooling / dehumidifying / heating mode, the opening degree of the air mix door 54, the inside / outside air switching device 53, and the operation of the blowing mode door are controlled in the same manner as in the single cooling mode. In addition, the control device 60 appropriately controls the operation of other control target devices.

[0296] Therefore, in the heat pump cycle 10a in the cooling / dehumidifying / heating mode, a vapor compression refrigeration cycle is configured in which the water-refrigerant heat exchanger 141 functions as a condenser, and the indoor evaporator 18 and the chiller 20 function as evaporators.

[0297] In the low-temperature side heat medium circuit 30a in the cooling / dehumidifying / heating mode, the low-temperature side heat medium pumped from the low-temperature side pump 31 flows into the chiller 20 and is cooled. The low-temperature side heat medium cooled in the chiller 20 flows into the cooling water passage 80a of the battery 80 and the low-temperature side radiator 34 in response to the operation of the low-temperature side flow control valve 32.

[0298] The low-temperature side heat medium cooled by the chiller 20 flows through the coolant passage 80a of the battery 80, thereby cooling the battery 80. The low-temperature side heat medium that flows into the low-temperature side radiator 34 exchanges heat with the outside air and absorbs heat from the outside air.

[0299] In the high-temperature side heat medium circuit 40 in the cooling / dehumidifying / heating mode, the high-temperature side heat medium that flows into the high-temperature side radiator 44 is cooled by dissipating heat to the outside air, as in the single cooling mode. The high-temperature side heat medium that flows into the heater core 45 dissipates heat to the blown air.

[0300] In the interior air conditioning unit 50 in the cooling / dehumidifying / heating mode, temperature-adjusted ventilation air is blown into the vehicle compartment, as in the single dehumidifying / heating mode, thereby realizing dehumidifying and heating the vehicle compartment.

[0301] (d-1) Standalone heating mode In the heat pump cycle 10a in the single heating mode, the controller 60 fully closes the cooling expansion valve 15b, throttles the cooling expansion valve 15c, and fully closes the hot gas flow rate control valve 15d.

[0302] Therefore, in the heat pump cycle 10a in the sole heating mode, the refrigerant discharged from the compressor 11 is switched to a refrigerant circuit in which it circulates in the order of the water-refrigerant heat exchanger 141, the cooling expansion valve 15c in the throttling state, the chiller 20, and the suction port of the compressor 11.

[0303] In the low-temperature side heat medium circuit 30a in the single heating mode, the operations of the low-temperature side pump 31 and the low-temperature side flow rate adjustment valve 32 are controlled in the same manner as in the single dehumidification heating mode.

[0304] In the high-temperature side heat medium circuit 40 in the single heating mode, the operations of the high-temperature side pump 41 and the high-temperature side flow rate adjustment valve 42 are controlled in the same manner as in the single cooling mode.

[0305] In the heating mode for heating the vehicle interior, the amount of heat dissipated from the high-temperature side heat medium to the blown air in the heater core 45 is greater than in the cooling mode or the dehumidification heating mode. For this reason, the high-temperature side flow rate adjustment valve 42 in the heating mode often causes almost the entire flow rate of the high-temperature side heat medium flowing out from the high-temperature side heat medium outlet 111q to flow toward the heater core 45.

[0306] In the indoor air conditioning unit 50 in the single heating mode, the opening degree of the air mix door 54, the inside / outside air switching device 53, and the operation of the blowing mode door are controlled in the same manner as in the single cooling mode. In addition, the control device 60 appropriately controls the operation of other control target devices.

[0307] Therefore, in the heat pump cycle 10a in the single heating mode, a vapor compression refrigeration cycle is configured in which the water-refrigerant heat exchanger 141 functions as a condenser and the chiller 20 functions as an evaporator.

[0308] In the low-temperature side heat medium circuit 30a in the single heating mode, as in the single dehumidification heating mode, the low-temperature side heat medium cooled by the chiller 20 flows into the low-temperature side radiator 34. In the low-temperature side radiator 34, the low-temperature side heat medium exchanges heat with the outside air and absorbs heat from the outside air.

[0309] In the high-temperature side heat medium circuit 40 in the sole heating mode, the high-temperature side heat medium that flows into the high-temperature side radiator 44 is cooled by dissipating heat to the outside air, as in the sole cooling mode. The high-temperature side heat medium that flows into the heater core 45 dissipates heat to the blown air.

[0310] In the interior air conditioning unit 50 in the single heating mode, the blown air sent from the interior blower 52 passes through the interior evaporator 18. The blown air that has passed through the interior evaporator 18 is reheated in the interior condenser 14 so as to approach the target blown air temperature TAO according to the opening degree of the air mix door 54. Then, the temperature-adjusted blown air is blown into the vehicle cabin, thereby heating the vehicle cabin.

[0311] (d-2) Cooling and heating mode In the heat pump cycle 10a in the cooling / heating mode, the controller 60 fully closes the cooling expansion valve 15b, throttles the cooling expansion valve 15c, and fully closes the hot gas flow rate control valve 15d.

[0312] Therefore, in the heat pump cycle 10a in the cooling / heating mode, the refrigerant circuit is switched to the same refrigerant circuit as in the single heating mode.

[0313] In the low-temperature side heat medium circuit 30a in the cooling and heating mode, the operations of the low-temperature side pump 31 and the low-temperature side flow rate adjustment valve 32 are controlled in the same manner as in the cooling and dehumidifying heating mode.

[0314] In the high-temperature side heat medium circuit 40 in the cooling / heating mode, the operations of the high-temperature side pump 41 and the high-temperature side flow rate adjustment valve 42 are controlled in the same manner as in the single cooling mode.

[0315] In the indoor air conditioning unit 50 in the cooling / heating mode, the opening degree of the air mix door 54, the inside / outside air switching device 53, and the operation of the blowing mode door are controlled in the same manner as in the single cooling mode. In addition, the control device 60 appropriately controls the operation of other control target devices.

[0316] Therefore, in the heat pump cycle 10a in the cooling / heating mode, a vapor compression refrigeration cycle is configured in which the water-refrigerant heat exchanger 141 functions as a condenser and the chiller 20 functions as an evaporator.

[0317] In the low-temperature side heat medium circuit 30a in the cooling and heating mode, as in the cooling and dehumidifying heating mode, the low-temperature side heat medium cooled in the chiller 20 flows through the coolant passage 80a of the battery 80 to cool the battery 80. The low-temperature side heat medium that flows into the low-temperature side radiator 34 exchanges heat with the outside air and absorbs heat from the outside air.

[0318] In the high-temperature side heat medium circuit 40 in the cooling / heating mode, the high-temperature side heat medium that flows into the high-temperature side radiator 44 is cooled by dissipating heat to the outside air, as in the single cooling mode. The high-temperature side heat medium that flows into the heater core 45 dissipates heat to the blown air.

[0319] In the interior air conditioning unit 50 in the cooling / heating mode, temperature-adjusted ventilation air is blown into the vehicle compartment, similarly to the cooling / heating mode, thereby heating the vehicle compartment.

[0320] (e-1) Hot gas heating mode In the hot gas heating mode, the controller 60 fully closes the cooling expansion valve 15b, throttles the cooling expansion valve 15c, and throttles the hot gas flow rate adjustment valve 15d.

[0321] For this reason, in the heat pump cycle 10a in the hot gas heating mode, the refrigerant discharged from the compressor 11 circulates in the order of the water-refrigerant heat exchanger 141, the cooling expansion valve 15c in the throttled state, the chiller 20, and the suction port of the compressor 11. At the same time, the refrigerant discharged from the compressor 11 is switched to a refrigerant circuit in which the refrigerant circulates in the order of the hot gas flow rate control valve 15d of the hot gas passage 22a in the throttled state, the chiller 20, and the suction port of the compressor 11.

[0322] Furthermore, in the low-temperature side heat medium circuit 30a in the hot gas heating mode, the low-temperature side pump 31 is stopped.

[0323] In the high-temperature side heat medium circuit 40 in the hot gas heating mode, the control device 60 operates the high-temperature side pump 41 so as to exert a predetermined reference pumping capacity. Furthermore, the control device 60 controls the operation of the high-temperature side flow rate adjustment valve 42 so that the entire flow rate of the high-temperature side heat medium flowing out from the high-temperature side heat medium outlet 111q flows to the heater core 45 side.

[0324] For this reason, in the high-temperature side heat medium circuit 40 in the hot gas heating mode, the circuit configuration is switched to one in which the high-temperature side heat medium pumped from the high-temperature side pump 41 circulates through the heat medium passage of the water-refrigerant heat exchanger 141, the heater core 45, and the suction port of the high-temperature side pump 41 in that order.

[0325] In the indoor air conditioning unit 50 in the hot gas heating mode, the opening degree of the air mix door 54, the inside / outside air switching device 53, and the operation of the blowing mode door are controlled in the same manner as in the single cooling mode. In addition, the control device 60 appropriately controls the operation of other control target devices.

[0326] Therefore, in the heat pump cycle 10a in the hot gas heating mode, the flow of the refrigerant discharged from the compressor 11 is branched at the first inner three-way joint portion 13a.

[0327] One of the refrigerants branched at the first internal three-way joint 13a flows into the water-refrigerant heat exchanger 141 and dissipates heat to the high-temperature side heat medium. This heats the high-temperature side heat medium. The refrigerant flowing out of the water-refrigerant heat exchanger 141 flows into the cooling expansion valve 15c and is reduced in pressure. The refrigerant with a relatively low enthalpy reduced in pressure by the cooling expansion valve 15c flows into the chiller 20.

[0328] On the other hand, the other refrigerant branched at the first internal three-way joint portion 13a is depressurized by adjusting the flow rate at the hot gas flow rate adjustment valve 15d. The refrigerant with a relatively high enthalpy depressurized at the hot gas flow rate adjustment valve 15d flows into the chiller 20.

[0329] In the chiller 20, the refrigerant decompressed by the cooling expansion valve 15c and the refrigerant decompressed by the hot gas flow rate control valve 15d are mixed. At this time, since the low-temperature side pump 31 is stopped, there is no heat exchange between the refrigerant and the low-temperature side heat medium in the chiller 20. The refrigerant flowing out of the chiller 20 is sucked into the compressor 11 and compressed again.

[0330] In the high-temperature side heat medium circuit 40 in the hot gas heating mode, the high-temperature side heat medium that has flowed into the heater core 45 dissipates heat to the blown air.

[0331] In the interior air conditioning unit 50 in the hot gas heating mode, the ventilation air blown from the interior blower 52 passes through the interior evaporator 18. The ventilation air that has passed through the interior evaporator 18 is heated by the heater core 45 according to the opening degree of the air mix door 54. Then, the ventilation air heated by the heater core 45 is blown into the vehicle cabin, thereby heating the vehicle cabin.

[0332] (e-2) Warm-up hot gas heating mode In the low-temperature side heat medium circuit 30a in the warm-up hot gas heating mode, the controller 60 controls the operation of the low-temperature side pump 31 and the low-temperature side flow rate adjustment valve 32 in the same manner as in the cooling / air-conditioning mode. Therefore, in the low-temperature side heat medium circuit 30a, the circuit configuration is switched to one in which the low-temperature side heat medium pumped by the low-temperature side pump 31 circulates through the chiller 20, the cooling water passage 80a of the battery 80, and the suction port of the low-temperature side pump 31 in that order. Other operations are the same as in the hot gas heating mode.

[0333] Therefore, in the heat pump cycle 10a in the warm-up hot gas heating mode, the refrigerant that flows into the chiller 20 releases heat to the low-temperature side heat medium. This heats the low-temperature side heat medium. In the low-temperature side heat medium circuit 30 in the warm-up hot gas heating mode, the low-temperature side heat medium heated by the chiller 20 flows through the coolant passage 80a of the battery 80. This warms up the battery 80.

[0334] (f) Single cooling mode In the heat pump cycle 10a in the single cooling mode, the controller 60 fully closes the cooling expansion valve 15b, throttles the cooling expansion valve 15c, and fully closes the hot gas flow rate control valve 15d.

[0335] For this reason, in the heat pump cycle 10a in the sole cooling mode, as in the sole heating mode, the refrigerant discharged from the compressor 11 is switched to a refrigerant circuit in which it circulates in the order of the water-refrigerant heat exchanger 141, the cooling expansion valve 15c in the throttling state, the chiller 20, and the suction port of the compressor 11.

[0336] In the low-temperature side heat medium circuit 30a in the single cooling mode, the operations of the low-temperature side pump 31 and the low-temperature side flow rate adjustment valve 32 are controlled in the same manner as in the cooling / air-cooling mode.

[0337] For this reason, in the low-temperature side heat medium circuit 30a in the single cooling mode, the control device 60 switches to a circuit configuration in which the low-temperature side heat medium pumped by the low-temperature side pump 31 circulates through the chiller 20, the cooling water passage 80a of the battery 80, and the suction port of the low-temperature side pump 31 in that order.

[0338] In the high-temperature side heat medium circuit 40 in the single cooling mode, the high-temperature side pump 41 is operated to exert a predetermined reference pumping capacity. Furthermore, the operation of the high-temperature side flow rate adjustment valve 42 is controlled so that the entire flow rate of the high-temperature side heat medium flowing out from the high-temperature side heat medium outlet 111q flows to the high-temperature side radiator 44 side.

[0339] For this reason, in the high-temperature side heat medium circuit 40 in the single cooling mode, the circuit configuration is switched to one in which the high-temperature side heat medium pumped from the high-temperature side pump 41 circulates through the water-refrigerant heat exchanger 141, the high-temperature side radiator 44, and the suction port of the high-temperature side pump 41 in that order.

[0340] Therefore, in the heat pump cycle 10a in the single cooling mode, a vapor compression refrigeration cycle is configured in which the water-refrigerant heat exchanger 141 functions as a condenser and the chiller 20 functions as an evaporator.

[0341] In the low-temperature side heat medium circuit 30a in the single cooling mode, the low-temperature side heat medium cooled in the chiller 20 flows through the coolant passage 80a of the battery 80, as in the cooling / air-cooling mode, thereby cooling the battery 80.

[0342] In the high-temperature side heat medium circuit 40 in the single cooling mode, the high-temperature side heat medium pumped from the high-temperature side pump 41 is heated in the water-refrigerant heat exchanger 141. The high-temperature side heat medium heated in the water-refrigerant heat exchanger 141 flows into the high-temperature side radiator 44. The high-temperature side heat medium that flows into the high-temperature side radiator 44 dissipates heat to the outside air and is cooled.

[0343] As described above, in the vehicle air conditioner 1a of this embodiment, by switching the operation mode, it is possible to perform comfortable air conditioning for the vehicle interior and appropriate temperature adjustment of the battery 80, which is an on-board device.

[0344] In addition, in the heat pump cycle 10a of the present embodiment, a subcooling type heat exchanger is used as the water-refrigerant heat exchanger 141. Furthermore, the refrigerant flowing out of the heat exchanger functioning as an evaporator can be a refrigerant having a degree of subcooling. As a result, the amount of heat absorbed by the heat exchanger functioning as an evaporator can be increased, and the coefficient of performance (COP) of the cycle can be improved.

[0345] Furthermore, in this embodiment, since the compressor module 110 is employed, the same effects as those of the first embodiment can be obtained. That is, the noise of the compressor 11 can be sufficiently suppressed without causing a decrease in productivity of the vehicle air conditioner 1a, which is a heat pump cycle device.

[0346] Furthermore, in the compressor module 110 of this embodiment, heat of the high-pressure side refrigerant in the receiver portion 141b, which is the high-pressure side refrigerant device, can be transferred to the vibration-proof rubber 11c to heat the vibration-proof rubber 11c.

[0347] According to this, even when the outside air temperature is low, the vibration-proof rubber 11c can be heated to suppress a decrease in the elasticity of the vibration-proof rubber 11c. Therefore, it is possible to effectively suppress the vibration of the compressor 11 from being transmitted to the flow path box 111 or the cover member, which would otherwise cause the flow path box 111 or the cover member to generate noise.

[0348] Third embodiment In this embodiment, an example will be described in which a compressor module 120 according to the present invention is applied to a vehicle air conditioner 1b shown in the overall configuration diagram of Fig. 8. The vehicle air conditioner 1b is a heat pump cycle device that performs air conditioning in the vehicle cabin and temperature adjustment of on-board equipment, similar to the vehicle air conditioner 1 described in the first embodiment.

[0349] The vehicle air conditioner 1b includes a heat pump cycle 10b, a low-temperature side heat medium circuit 30, and an interior air conditioning unit 50.

[0350] In the heat pump cycle 10b of this embodiment, the muffler section 12, the evaporation pressure control valve 19, the accumulator section 21, the dehumidification passage 22b, the dehumidification on-off valve 23a, etc. are eliminated from the heat pump cycle 10 described in the first embodiment. Furthermore, the heat pump cycle 10b employs a receiver section 24, an internal heat exchange section 26, and a thermostatic expansion valve 27.

[0351] The compressor module 120 is a component that integrates a plurality of components that mainly constitute the heat pump cycle 10b. In the compressor module 120 of the present embodiment, the components surrounded by the dashed line in FIG. 8 are integrated.

[0352] More specifically, in the compressor module 120 of this embodiment, the following components of the heat pump cycle 10b are integrated together: the compressor 11, the heating expansion valve 15a, the cooling expansion valve 15c, the hot gas flow control valve 15d, the outdoor unit pressure control valve 19b, the chiller 20, the first on-off valve 23c, the second on-off valve 23d, the receiver section 24, the first fixed throttle 25a, the second fixed throttle 25b, and the internal heat exchange section 26.

[0353] Of these components, the compressor 11, the heating expansion valve 15a, the cooling expansion valve 15c, the hot gas flow control valve 15d, the outdoor unit pressure control valve 19b, the chiller 20, the first on-off valve 23c, and the second on-off valve 23d are integrated by being attached to the flow path box 121 of the compressor module 120.

[0354] The receiver section 24, the first fixed throttle 25a, the second fixed throttle 25b, and the internal heat exchange section 26 are integrally formed in the flow path box 121. The flow path box 121 is a mounting member and a passage forming member similar to the flow path box 101 described in the first embodiment.

[0355] As in the first embodiment, a compressor-side inlet 121b formed in a flow path box 121 is connected to a discharge port of the compressor 11 of the heat pump cycle 10b via a high-pressure hose 11b. The compressor-side inlet 121b is connected to an inlet of the first internal three-way joint portion 13a via an internal refrigerant passage.

[0356] One of the outlets of the first internal three-way joint 13a is connected through an internal refrigerant passage to a condenser-side outlet 121c formed in the flow path box 121. The other of the outlets of the first internal three-way joint 13a is connected through a hot gas passage 22a to one of the inlets of a fourth internal three-way joint 13d. As in the first embodiment, a hot gas flow rate control valve 15d is disposed in the hot gas passage 22a.

[0357] A refrigerant outlet of the indoor condenser 14 of the heat pump cycle 10b is connected to a condenser-side inlet 121d formed in the flow path box 121. The condenser-side inlet 121d is connected to an inlet of the eighth internal three-way joint portion 13h via an internal refrigerant passage.

[0358] One of the outlets of the eighth internal three-way joint 13h is connected to one of the inlets of the ninth internal three-way joint 13i through an internal refrigerant passage. The other of the outlets of the eighth internal three-way joint 13h is connected to one of the inlets of the tenth internal three-way joint 13j through an internal refrigerant passage. The internal heat medium passage extending from the other outlet of the eighth internal three-way joint 13h to the inlet of the receiver 24 is the inlet-side passage 22d.

[0359] A first on-off valve 23c and a first fixed throttle 25a are arranged in the inlet-side passage 22d. The first on-off valve 23c is an on-off valve that opens and closes the inlet-side passage 22d. The basic configuration of the first on-off valve 23c is similar to that of the dehumidification on-off valve 23a and the like described in the first embodiment. Therefore, the first on-off valve 23c is an electric device and a refrigerant circuit switching unit. The first fixed throttle 25a is a pressure reducing unit that reduces the pressure of the refrigerant flowing into the receiver unit 24. An orifice, a capillary tube, or the like can be used as the first fixed throttle 25a.

[0360] An outlet of the tenth internal three-way joint section 13j is connected to an inlet of a receiver section 24 formed in the flow path box 121. The receiver section 24 is a high-pressure side gas-liquid separation section that separates the refrigerant flowing out from the heat exchange section functioning as a condenser into gas and liquid phases and stores the separated liquid phase refrigerant as surplus refrigerant for the cycle.

[0361] The outlet of the receiver section 24 is connected to the inlet of the eleventh inner three-way joint section 13k via an internal refrigerant passage. One outlet of the eleventh inner three-way joint section 13k is connected to the inlet of the seventh inner three-way joint section 13g via an internal refrigerant passage. The other outlet of the eleventh inner three-way joint section 13k is connected to the other inlet of the ninth inner three-way joint section 13i via an internal refrigerant passage.

[0362] The internal heat medium passage from the other outlet of the eleventh internal three-way joint portion 13k to the ninth internal three-way joint portion 13i is the outlet-side passage 22e. A third check valve 17c is disposed in the outlet-side passage 22e. The third check valve 17c allows the refrigerant to flow from the eleventh internal three-way joint portion 13k side to the ninth internal three-way joint portion 13i side, and prohibits the refrigerant from flowing from the ninth internal three-way joint portion 13i side to the eleventh internal three-way joint portion 13k side.

[0363] A second on-off valve 23d is disposed in the internal refrigerant passage extending from one outlet of the eighth internal three-way joint 13h to one inlet of the ninth internal three-way joint 13i. The second on-off valve 23d is an on-off valve that opens and closes the internal refrigerant passage extending from the eighth internal three-way joint 13h to the ninth internal three-way joint 13i. The basic configuration of the second on-off valve 23d is the same as that of the first on-off valve 23c. Therefore, the second on-off valve 23d is an electric device and a refrigerant circuit switching unit.

[0364] The outlet of the eighth internal three-way joint portion 13h is connected, via an internal refrigerant passage, to an outdoor unit side outlet 121e formed in the flow path box 121. A heating expansion valve 15a is disposed in the internal refrigerant passage extending from the outlet of the eighth internal three-way joint portion 13h to the outdoor unit side outlet 121e.

[0365] The outdoor unit side outlet 121e is connected to the refrigerant inlet side of the outdoor heat exchanger 16. The outdoor unit side inlet 121f formed in the flow path box 121 is connected to the refrigerant outlet of the outdoor heat exchanger 16. The outdoor unit side inlet 101f is connected to the inlet of the third internal three-way joint portion 13c via an internal refrigerant passage.

[0366] One of the outlets of the third inner three-way joint portion 13c communicates with the other inlet of the tenth inner three-way joint portion 13j through an internal refrigerant passage. The other of the outlets of the third inner three-way joint portion 13c communicates with one of the inlet of the sixth inner three-way joint portion 13f through a heating passage 22c.

[0367] The outdoor unit pressure regulating valve 19b, the twelfth internal three-way joint 13m, and the second check valve 17b are arranged in the heating passage 22c. The outdoor unit pressure regulating valve 19b is an electric variable throttle mechanism that adjusts the refrigerant pressure in the outdoor heat exchanger 16. The basic configuration of the outdoor unit pressure regulating valve 19b is similar to that of the cooling expansion valve 15c. Therefore, the cooling expansion valve 15c is an electric device. The cooling expansion valve 15c has a fully closing function.

[0368] The second check valve 17b in this embodiment allows the refrigerant to flow from the 12th internal three-way joint portion 13m side to the sixth internal three-way joint portion 13f side, and prohibits the refrigerant from flowing from the sixth internal three-way joint portion 13f side to the 12th internal three-way joint portion 13m side.

[0369] One of the outlets of the seventh internal three-way joint 13g is connected through an internal refrigerant passage to an inlet of a high-pressure side passage of an internal heat exchanger 26 formed in the flow path box 121. The internal heat exchanger 26 is a heat exchanger that exchanges heat between the refrigerant flowing through the high-pressure side passage and the refrigerant flowing through the low-pressure side passage. More specifically, the internal heat exchanger 26 exchanges heat between the high-pressure side refrigerant flowing out of the receiver 24 and the low-pressure side refrigerant flowing out of the indoor evaporator 18 during the cooling mode or the like.

[0370] An outlet of the high-pressure side passage of the internal heat exchanger 26 is connected to an evaporator-side outlet 121g formed in the flow path box 121 through an internal refrigerant passage. The evaporator-side outlet 121g is connected to an inlet side of a thermostatic expansion valve 27. The thermostatic expansion valve 27 is an evaporator pressure reducing section that reduces the pressure of the refrigerant flowing out from one outlet of the internal four-way joint 13x during a cooling mode, which will be described later, and adjusts the flow rate of the refrigerant flowing out to the downstream side, similar to the cooling expansion valve 15b described in the first embodiment.

[0371] The thermal expansion valve 27 is configured with a mechanical mechanism. The thermal expansion valve 27 has a temperature sensing part having a deformable member (specifically, a diaphragm) that deforms according to the temperature and pressure of the refrigerant on the outlet side of the indoor evaporator 18, and a valve body part that displaces according to the deformation of the deformable member to change the throttle opening.

[0372] In the thermal expansion valve 27, the throttle opening is changed so that the degree of superheat of the refrigerant on the outlet side of the indoor evaporator 18 approaches a predetermined reference degree of superheat (5°C in this embodiment). When the temperature sensing part becomes extremely cold, the deformation member displaces the valve body part to the side that closes the throttle passage.

[0373] The outlet of the thermal expansion valve 27 is connected to the refrigerant inlet side of the indoor evaporator 18. The refrigerant outlet of the indoor evaporator 18 is connected to an evaporator side inlet 121h formed in the flow path box 121 via a passage for a temperature sensing part of the thermal expansion valve 27.

[0374] The evaporator side inlet 121h is connected via an internal refrigerant passage to an inlet of a low-pressure side passage of the internal heat exchanger 26. The outlet of the low-pressure side passage of the internal heat exchanger 26 is connected via an internal refrigerant passage to the other inlet of the twelfth internal three-way joint 13m.

[0375] The other outlet of the seventh internal three-way joint 13g is connected to the other inlet of the fourth internal three-way joint 13d via an internal refrigerant passage. As in the first embodiment, a cooling expansion valve 15c is disposed in the internal refrigerant passage extending from the other outlet of the seventh internal three-way joint 13g to the other inlet of the fourth internal three-way joint 13d.

[0376] An outlet of the fourth internal three-way joint portion 13d is connected to a chiller-side outlet 121i formed in the flow path box 121. A refrigerant inlet of the chiller 20 is directly connected to the chiller-side outlet 121i. A refrigerant outlet of the chiller 20 is directly connected to a chiller-side inlet 121j formed in the flow path box 121. The rest of the configuration of the heat pump cycle 10b is similar to that of the heat pump cycle 10 described in the first embodiment.

[0377] Next, a detailed configuration of the compressor module 120 will be described with reference to Fig. 9 and Fig. 10. The basic configuration of the compressor module 120 is similar to that of the compressor module 100 described in the first embodiment. As shown in Fig. 9, the compressor module 120 includes a metal flow path box 121. Also, as shown in Fig. 10, the compressor module 120 includes a resin cover member 122.

[0378] As in the first embodiment, the cover member 122 is attached to the flow path box 121 to form an accommodation space 123, which is an enclosed space for accommodating the compressor 11 and the like, inside the compressor module 120. Furthermore, as in the first embodiment, a heat insulating material 124 is arranged on the outer surface of the compressor module 120.

[0379] 9, the compressor 11 is accommodated inside the accommodation space 123. Therefore, the compressor side outlet 121a and the compressor side inlet 121b are formed inside the accommodation space 123. More specifically, the compressor side outlet 121a and the compressor side inlet 121b are formed on the inner side surface of the flow path box 121 on the accommodation space 123 side, and thus are formed inside the accommodation space 123.

[0380] 10, the indoor condenser 14, the heating expansion valve 15a, the cooling expansion valve 15c, the hot gas flow rate control valve 15d, the outdoor heat exchanger 16, the indoor evaporator 18, the outdoor evaporator pressure control valve 19b, the chiller 20, the first on-off valve 23c, and the second on-off valve 23d are disposed outside the accommodation space 123. Therefore, the indoor condenser 14, the outdoor heat exchanger 16, the indoor evaporator 18, and the chiller 20 in this embodiment are external components.

[0381] The condenser side outlet 121c, the condenser side inlet 121d, the outdoor unit side outlet 121e, the outdoor unit side inlet 121f, the evaporator side outlet 121g, the evaporator side inlet 121h, the chiller side outlet 121i, and the chiller side outlet 121j are formed on the outer surface of the flow path box 101, and thereby are formed outside the storage space 123.

[0382] Therefore, in this embodiment, the condenser side outlet 121c, the condenser side inlet 121d, the outdoor unit side outlet 121e, the outdoor unit side inlet 121f, the evaporator side outlet 121g, the evaporator side inlet 121h, the chiller side outlet 121i, and the chiller side outlet 121j are external connection ports to which the inlet and outlet sides of external component equipment are connected.

[0383] In addition, as in the first embodiment, the compressor 11 is fixed to multiple (four in this embodiment) fixing portions 121s formed on the bottom surface that forms the storage space 123 of the flow path box 121 via vibration-proof rubber 11c.

[0384] Moreover, the receiver unit 24 is formed on a side surface of the flow path box 121. The internal heat exchange unit 26 is formed on a bottom surface of the flow path box 121. Specifically, inside the bottom surface of the flow path box 121, a high-pressure side passage and a low-pressure side passage are formed to be disposed close to each other, so that the high-pressure side refrigerant and the low-pressure side refrigerant can exchange heat with each other.

[0385] The chiller 20 is fixed to the flow path box 101 by fitting the refrigerant inlet and outlet formed to protrude to the outside into the refrigerant inlet and outlet (i.e., the chiller side outlet 101i and the chiller side inlet 101j) formed in the flow path box 101. The heat medium piping of the low-temperature side heat medium circuit 30 is directly connected to the heat medium inlet and outlet of the chiller 20.

[0386] Other configurations of the vehicle air conditioner 1b are similar to those of the vehicle air conditioner 1 described in the first embodiment.

[0387] Next, the operation of the vehicle air conditioner 1b of this embodiment with the above configuration will be described. In the vehicle air conditioner 1b, similar to the vehicle air conditioner 1 described in the first embodiment, various operation modes are switched to perform air conditioning in the vehicle cabin and temperature adjustment of the battery 80. The detailed operation of each operation mode will be described below.

[0388] (a-1) Single cooling mode In the heat pump cycle 10b in the single cooling mode, the controller 60 fully opens the heating expansion valve 15a, fully closes the cooling expansion valve 15c, fully closes the hot gas flow control valve 15d, and fully closes the outdoor unit pressure control valve 19b. The controller 60 also closes the first on-off valve 23c and opens the second on-off valve 23d.

[0389] For this reason, in the heat pump cycle 10b in the cooling only mode, the refrigerant discharged from the compressor 11 is switched to a refrigerant circuit in which it circulates in the following order: the indoor condenser 14, the heating expansion valve 15a which is in a fully open state, the outdoor heat exchanger 16, the second fixed throttle 25b, the receiver section 24, the high-pressure side passage of the internal heat exchange section 26, the temperature-type expansion valve 27, the indoor evaporator 18, the low-pressure side passage of the internal heat exchange section 26, and the suction port of the compressor 11.

[0390] In the indoor air conditioning unit 50 in the single cooling mode, the opening degree of the air mix door 54 is controlled so that the blowing air temperature TAV approaches the target blowing temperature TAO, as in the single cooling mode of the first embodiment. In the indoor air conditioning unit 50 in the single cooling mode, the operation of the inside / outside air switching device 53 and the blowing mode door is controlled based on the target blowing temperature TAO. The control device 60 also controls the operation of other control target devices as appropriate.

[0391] Therefore, in the heat pump cycle 10b in the sole cooling mode, a vapor compression refrigeration cycle is configured in which the indoor condenser 14 and the outdoor heat exchanger 16 function as condensers and the indoor evaporator 18 functions as an evaporator.

[0392] In the interior air conditioning unit 50 in the single cooling mode, the blown air blown from the interior blower 52 is cooled by the interior evaporator 18. The blown air cooled by the interior evaporator 18 is reheated by the heater core 45 so as to approach the target blown air temperature TAO according to the opening degree of the air mix door 54. Then, the temperature-adjusted blown air is blown into the vehicle cabin, thereby cooling the vehicle cabin.

[0393] (a-2) Cooling mode In the heat pump cycle 10b in the cooling / air-cooling mode, the controller 60 controls the cooling expansion valve 15c to be in the throttling state in contrast to the single cooling mode.

[0394] Therefore, in the heat pump cycle 10b in the cooling / cooling mode, the refrigerant discharged from the compressor 11 circulates in the following order: the indoor condenser 14, the heating expansion valve 15a in the fully open state, the outdoor heat exchanger 16, the second fixed throttle 25b, the receiver section 24, the high-pressure side passage of the internal heat exchange section 26, the temperature-type expansion valve 27, the indoor evaporator 18, the low-pressure side passage of the internal heat exchange section 26, 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 following order: the indoor condenser 14, the heating expansion valve 15a in the fully open state, the outdoor heat exchanger 16, the second fixed throttle 25b, the receiver section 24, the cooling expansion valve 15c in the throttled state, the chiller 20, and the suction port of the compressor 11. In other words, the indoor evaporator 18 and the chiller 20 are switched to a refrigerant circuit in which the refrigerant flow is connected in parallel.

[0395] In the low-temperature side heat medium circuit 30 in the cooling / air-cooling mode, the control device 60 operates the low-temperature side pump 31 to exert a predetermined reference pumping capacity. Therefore, in the low-temperature side heat medium circuit 30, the low-temperature side heat medium pumped by the low-temperature side pump 31 circulates through the heat medium passage of the chiller 20, the cooling water passage 80a of the battery 80, and the suction port of the low-temperature side pump 31 in that order.

[0396] In the indoor air conditioning unit 50 in the cooling / cooling mode, the opening degree of the air mix door 54, the inside / outside air switching device 53, and the operation of the blowing mode door are controlled in the same manner as in the single cooling mode. In addition, the control device 60 appropriately controls the operation of other control target devices.

[0397] Therefore, in the heat pump cycle 10b in the cooling / air-conditioning mode, a vapor compression refrigeration cycle is configured in which the indoor condenser 14 and the outdoor heat exchanger 16 function as condensers, and the indoor evaporator 18 and the chiller 20 function as evaporators.

[0398] In the low-temperature side heat medium circuit 30 in the cooling / air-cooling mode, the low-temperature side heat medium pumped from the low-temperature side pump 31 flows into the chiller 20 and is cooled. Then, the low-temperature side heat medium cooled in the chiller 20 flows through the coolant passage 80a of the battery 80, thereby cooling the battery 80.

[0399] In the interior air conditioning unit 50 in the cooling / air-conditioning mode, temperature-adjusted air is blown into the vehicle compartment, thereby cooling the vehicle compartment, similarly to the single cooling mode.

[0400] (b-1) Single series dehumidification and heating mode In the heat pump cycle 10b in the single-serial dehumidification heating mode, the controller 60 throttles the heating expansion valve 15a, fully closes the cooling expansion valve 15c, fully closes the hot gas flow control valve 15d, and fully closes the outdoor unit pressure control valve 19b. The controller 60 also closes the first on-off valve 23c and opens the second on-off valve 23d.

[0401] For this reason, in the heat pump cycle 10b in the single-serial dehumidification heating mode, the refrigerant discharged from the compressor 11 is switched to a refrigerant circuit in which it circulates in the following order: the indoor condenser 14, the heating expansion valve 15a which is in a throttling state, the outdoor heat exchanger 16, the second fixed throttle 25b, the receiver section 24, the high-pressure side passage of the internal heat exchange section 26, the temperature-type expansion valve 27, the indoor evaporator 18, the low-pressure side passage of the internal heat exchange section 26, and the suction port of the compressor 11.

[0402] In the indoor air conditioning unit 50 in the single series dehumidifying and heating mode, the opening degree of the air mix door 54, the inside / outside air switching device 53, and the operation of the blowing mode door are controlled in the same manner as in the single cooling mode. In addition, the control device 60 appropriately controls the operation of other control target devices.

[0403] Therefore, in the heat pump cycle 10b in the single series dehumidifying and heating mode, a vapor compression refrigeration cycle is configured in which the indoor condenser 14 and the outdoor heat exchanger 16 function as condensers and the indoor evaporator 18 functions as an evaporator.

[0404] In the interior air conditioning unit 50 in the single serial dehumidifying and heating mode, the blown air blown from the interior blower 52 is cooled and dehumidified in the interior evaporator 18. The blown air cooled and dehumidified in the interior evaporator 18 is reheated in the interior condenser 14 so as to approach the target blown air temperature TAO according to the opening degree of the air mix door 54. Then, the temperature-adjusted blown air is blown into the vehicle cabin, thereby realizing dehumidifying and heating the vehicle cabin.

[0405] Here, since the vehicle air conditioner 1b of this embodiment has a receiver section 24, the series dehumidification heating mode is executed in a temperature range in which the saturation temperature of the refrigerant in the exterior heat exchanger 16 is higher than the outside air temperature Tam.

[0406] (b-2) Cooling series dehumidification heating mode In the heat pump cycle 10b in the cooling series dehumidification heating mode, the controller 60 controls the cooling expansion valve 15c to the throttling state, unlike the single series dehumidification heating mode.

[0407] Therefore, in the heat pump cycle 10b in the cooling serial dehumidification heating mode, the refrigerant discharged from the compressor 11 circulates in the same manner as in the single serial dehumidification heating mode. The refrigerant discharged from the compressor 11 is switched to a refrigerant circuit in which it circulates in the order of the indoor condenser 14, the heating expansion valve 15a in the throttling state, the outdoor heat exchanger 16, the second fixed throttle 25b, the receiver section 24, the cooling expansion valve 15c in the throttling state, the chiller 20, and the suction port of the compressor 11. In other words, the indoor evaporator 18 and the chiller 20 are switched to a refrigerant circuit in which they are connected in parallel with respect to the flow of the refrigerant.

[0408] In the cooling serial dehumidification heating mode, the operation of the low-temperature side pump 31 is controlled in the same manner as in the cooling cooling mode. Therefore, in the low-temperature side heat medium circuit 30 in the cooling serial dehumidification heating mode, the low-temperature side heat medium circulates in the same manner as in the cooling cooling mode.

[0409] Therefore, in the heat pump cycle 10b in the cooling serial dehumidification heating mode, a vapor compression refrigeration cycle is configured in which the indoor condenser 14 and the outdoor heat exchanger 16 function as condensers, and the indoor evaporator 18 and the chiller 20 function as evaporators.

[0410] In the low-temperature side heat medium circuit 30 in the cooling serial dehumidification heating mode, the low-temperature side heat medium cooled in the chiller 20 flows through the coolant passage 80a of the battery 80, thereby cooling the battery 80, as in the cooling and air-conditioning mode.

[0411] In the interior air conditioning unit 50 in the cooling series dehumidification heating mode, similarly to the single series dehumidification heating mode, temperature-adjusted ventilation air is blown into the vehicle compartment, thereby realizing dehumidification and heating of the vehicle compartment.

[0412] (c-1) Single parallel dehumidification and heating mode In the heat pump cycle 10b in the single-parallel dehumidification heating mode, the controller 60 controls the heating expansion valve 15a to be in a throttled state, the cooling expansion valve 15c to be in a fully closed state, the hot gas flow control valve 15d to be in a fully closed state, and the outdoor unit pressure control valve 19b to be in a fully opened or throttled state. The controller 60 also opens the first on-off valve 23c and closes the second on-off valve 23d.

[0413] Therefore, in the heat pump cycle 10b in the single dehumidification heating mode, the refrigerant discharged from the compressor 11 circulates in the following order: the indoor condenser 14, the inlet passage 22d, the receiver 24, the outlet passage 22e, the heating expansion valve 15a in the throttled state, the outdoor heat exchanger 16, the outdoor pressure control valve 19b of the heating passage 22c, and the suction port of the compressor 11. The refrigerant discharged from the compressor 11 circulates in the following order: the indoor condenser 14, the inlet passage 22d, the receiver 24, the high-pressure side passage of the internal heat exchanger 26, the thermostatic expansion valve 27, the indoor evaporator 18, the low-pressure side passage of the internal heat exchanger 26, and the suction port of the compressor 11. At the same time, the refrigerant circuit is switched to. In other words, the indoor evaporator 18 and the outdoor heat exchanger 16 are switched to a refrigerant circuit in which the refrigerant flow is connected in parallel.

[0414] In the indoor air conditioning unit 50 in the single dehumidification heating mode, the opening degree of the air mix door 54, the inside / outside air switching device 53, and the operation of the blowing mode door are controlled in the same manner as in the single cooling mode. In addition, the control device 60 appropriately controls the operation of other control target devices.

[0415] Therefore, in the heat pump cycle 10b in the single dehumidification heating mode, a vapor compression refrigeration cycle is configured in which the indoor condenser 14 functions as a condenser, and the outdoor heat exchanger 16 and the indoor evaporator 18 function as evaporators.

[0416] In the interior air conditioning unit 50 in the single dehumidification heating mode, the blown air blown from the interior blower 52 is cooled and dehumidified in the interior evaporator 18. The blown air cooled and dehumidified in the interior evaporator 18 is reheated in the interior condenser 14 so as to approach the target blown air temperature TAO according to the opening degree of the air mix door 54. Then, the temperature-adjusted blown air is blown into the vehicle cabin, thereby realizing dehumidification and heating of the vehicle cabin.

[0417] (c-2) Parallel cooling, dehumidification and heating mode In the heat pump cycle 10 in the cooling-parallel dehumidification-heating mode, the control device 60 controls the cooling expansion valve 15c to the throttling state, unlike in the single-parallel dehumidification-heating mode.

[0418] Therefore, in the heat pump cycle 10b in the cooling-parallel dehumidification-heating mode, the refrigerant discharged from the compressor 11 circulates in the same manner as in the single-parallel dehumidification-heating mode. At the same time, the refrigerant discharged from the compressor 11 is switched to a refrigerant circuit in which it circulates through the indoor condenser 14, the inlet-side passage 22d, the receiver 24, the cooling expansion valve 15c in the throttling state, the chiller 20, and the suction port of the compressor 11 in that order. In other words, the refrigerant circuit is switched to one in which the outdoor heat exchanger 16, the indoor evaporator 18, and the chiller 20 are connected in parallel with respect to the flow of the refrigerant.

[0419] In the cooling parallel dehumidification heating mode, the operation of the low-temperature side pump 31 is controlled in the same manner as in the cooling and cooling mode. Therefore, in the low-temperature side heat medium circuit 30 in the cooling parallel dehumidification heating mode, the low-temperature side heat medium circulates in the same manner as in the cooling and cooling mode.

[0420] In the indoor air conditioning unit 50 in the cooling parallel dehumidification heating mode, the opening degree of the air mix door 54, the inside / outside air switching device 53, and the operation of the blowing mode door are controlled in the same manner as in the single cooling mode. In addition, the control device 60 appropriately controls the operation of other control target devices.

[0421] Therefore, in the heat pump cycle 10 in the cooling parallel dehumidification heating mode, a vapor compression refrigeration cycle is configured in which the indoor condenser 14 functions as a condenser, and the outdoor heat exchanger 16, the indoor evaporator 18 and the chiller 20 function as evaporators.

[0422] In the low-temperature side heat medium circuit 30 in the cooling / dehumidifying / heating mode, the low-temperature side heat medium cooled in the chiller 20 flows through the coolant passage 80a of the battery 80, as in the cooling / cooling mode, thereby cooling the battery 80.

[0423] In the interior air conditioning unit 50 in the cooling / dehumidifying / heating mode, temperature-adjusted ventilation air is blown into the vehicle compartment, as in the single dehumidifying / heating mode, thereby realizing dehumidifying and heating the vehicle compartment.

[0424] (d-1) Standalone heating mode In the heat pump cycle 10b in the single heating mode, the controller 60 controls the heating expansion valve 15a to be in a throttled state, the cooling expansion valve 15c to be in a fully closed state, the hot gas flow control valve 15d to be in a fully closed state, and the outdoor unit pressure control valve 19b to be in a fully opened or throttled state. The controller 60 also opens the first opening / closing valve 23c and closes the second opening / closing valve 23d.

[0425] For this reason, in the heat pump cycle 10 in the sole heating mode, the refrigerant discharged from the compressor 11 is switched to a refrigerant circuit in which it circulates in the following order: the indoor condenser 14, the inlet side passage 22d, the receiver section 24, the outlet side passage 22e, the heating expansion valve 15a which is in a throttled state, the outdoor heat exchanger 16, the outdoor pressure regulating valve 19b of the heating passage 22c, and the suction port of the compressor 11.

[0426] In the indoor air conditioning unit 50 in the single heating mode, the opening degree of the air mix door 54, the inside / outside air switching device 53, and the operation of the blowing mode door are controlled in the same manner as in the single cooling mode. In addition, the control device 60 appropriately controls the operation of other control target devices.

[0427] Therefore, in the heat pump cycle 10 in the sole heating mode, a vapor compression refrigeration cycle is configured in which the indoor condenser 14 functions as a condenser and the outdoor heat exchanger 16 functions as an evaporator.

[0428] In the interior air conditioning unit 50 in the single heating mode, the blown air sent from the interior blower 52 passes through the interior evaporator 18. The blown air that has passed through the interior evaporator 18 is reheated in the interior condenser 14 so as to approach the target blown air temperature TAO according to the opening degree of the air mix door 54. Then, the temperature-adjusted blown air is blown into the vehicle cabin, thereby heating the vehicle cabin.

[0429] (d-2) Cooling and heating mode In the heat pump cycle 10 in the cooling / heating mode, the controller 60 controls the cooling expansion valve 15c to the throttling state, unlike the single heating mode.

[0430] Therefore, in the heat pump cycle 10 in the cooling and heating mode, the refrigerant discharged from the compressor 11 circulates in the same manner as in the single heating mode. 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 indoor condenser 14, the inlet side passage 22d, the receiver section 24, the cooling expansion valve 15c in the throttling state, the chiller 20, and the suction port of the compressor 11. In other words, the outdoor heat exchanger 16 and the chiller 20 are switched to a refrigerant circuit in which they are connected in parallel with respect to the flow of the refrigerant.

[0431] In the cooling parallel dehumidification heating mode, the operation of the low-temperature side pump 31 is controlled in the same manner as in the cooling cooling mode. Therefore, in the low-temperature side heat medium circuit 30 in the cooling series dehumidification heating mode, the low-temperature side heat medium circulates in the same manner as in the cooling cooling mode.

[0432] In the indoor air conditioning unit 50 in the cooling parallel dehumidification heating mode, the opening degree of the air mix door 54, the inside / outside air switching device 53, and the operation of the blowing mode door are controlled in the same manner as in the single cooling mode. In addition, the control device 60 appropriately controls the operation of other control target devices.

[0433] Therefore, in the heat pump cycle 10 in the cooling / heating mode, a vapor compression refrigeration cycle is configured in which the indoor condenser 14 functions as a condenser, and the outdoor heat exchanger 16 and the chiller 20 function as evaporators.

[0434] In the low-temperature side heat medium circuit 30 in the cooling / heating mode, the low-temperature side heat medium cooled in the chiller 20 flows through the coolant passage 80a of the battery 80, as in the cooling / air-cooling mode, thereby cooling the battery 80.

[0435] In the interior air conditioning unit 50 in the cooling / heating mode, similarly to the single heating mode, temperature-adjusted ventilation air is blown into the vehicle compartment, thereby heating the vehicle compartment.

[0436] (e-1) Hot gas heating mode In the hot gas heating mode, the controller 60 fully closes the heating expansion valve 15a, throttles the cooling expansion valve 15c, throttles the hot gas flow control valve 15d, and fully closes the outdoor unit pressure control valve 19b. The controller 60 also opens the first opening / closing valve 23c and closes the second opening / closing valve 23d.

[0437] For this reason, in the heat pump cycle 10b in the hot gas heating mode, the refrigerant discharged from the compressor 11 circulates in the following order: the indoor condenser 14, the inlet side passage 22d, the receiver 24, the cooling expansion valve 15c in the throttled state, the chiller 20, and the suction port of the compressor 11. At the same time, the refrigerant discharged from the compressor 11 is switched to a refrigerant circuit in which the refrigerant circulates in the following order: the hot gas flow rate control valve 15d of the hot gas passage 22a in the throttled state, the chiller 20, and the suction port of the compressor 11.

[0438] In the hot gas heating mode, the low-temperature side pump 31 is stopped in the low-temperature side heat medium circuit 30. In the hot gas heating mode, the indoor air conditioning unit 50 controls the operation of the air mix door 54, the inside / outside air switching device 53, and the blowing mode door in the same manner as in the single cooling mode. The control device 60 also controls the operation of other control target devices as appropriate.

[0439] Therefore, in the heat pump cycle 10b in the hot gas heating mode, the flow of the refrigerant discharged from the compressor 11 is branched at the first inner three-way joint portion 13a.

[0440] One of the refrigerant branches at the first internal three-way joint 13a flows into the indoor condenser 14 and dissipates heat to the blown air. This heats the blown air. The refrigerant flowing out of the indoor condenser 14 flows into the receiver 24 via the inlet passage 22d. The refrigerant flowing out of the receiver 24 flows into the cooling expansion valve 15c and is reduced in pressure.

[0441] The refrigerant with a relatively low enthalpy, which has been decompressed by the cooling expansion valve 15c, flows into the chiller 20 via the fourth internal three-way joint 13d. Here, the thermostatic expansion valve 27 is fully closed when the outside air temperature is low. Therefore, the refrigerant does not flow out from the receiver section 24 to the internal heat exchange section 26.

[0442] On the other hand, the other refrigerant branched at the first internal three-way joint portion 13a is depressurized by adjusting the flow rate at the hot gas flow rate adjustment valve 15d. The refrigerant with a relatively high enthalpy depressurized at the hot gas flow rate adjustment valve 15d flows into the chiller 20.

[0443] In the chiller 20, the refrigerant decompressed by the cooling expansion valve 15c and the refrigerant decompressed by the hot gas flow rate control valve 15d are mixed. At this time, since the low-temperature side pump 31 is stopped, there is no heat exchange between the refrigerant and the low-temperature side heat medium in the chiller 20. The refrigerant flowing out of the chiller 20 is sucked into the compressor 11 and compressed again.

[0444] In the high-temperature side heat medium circuit 40 in the hot gas heating mode, the high-temperature side heat medium that has flowed into the heater core 45 dissipates heat to the blown air.

[0445] In the interior air conditioning unit 50 in the hot gas heating mode, the ventilation air blown from the interior blower 52 passes through the interior evaporator 18. The ventilation air that has passed through the interior evaporator 18 is heated by the heater core 45 according to the opening degree of the air mix door 54. Then, the ventilation air heated by the heater core 45 is blown into the vehicle cabin, thereby heating the vehicle cabin.

[0446] (e-2) Warm-up hot gas heating mode In the low-temperature side heat medium circuit 30 in the warm-up hot gas heating mode, the control device 60 operates the low-temperature side pump 31 so as to exert a predetermined reference pumping capacity. Therefore, in the low-temperature side heat medium circuit 30, the low-temperature side heat medium pumped by the low-temperature side pump 31 circulates through the heat medium passage of the chiller 20 and then through the cooling water passage 80a of the battery 80. Other operations are the same as in the hot gas heating mode.

[0447] Therefore, in the heat pump cycle 10b in the warm-up hot gas heating mode, the refrigerant that has flowed into the chiller 20 releases heat to the low-temperature side heat medium. This heats the low-temperature side heat medium. In the low-temperature side heat medium circuit 30 in the warm-up hot gas heating mode, the low-temperature side heat medium heated by the chiller 20 flows through the coolant passage 80a of the battery 80. This warms up the battery 80.

[0448] (f) Single cooling mode In the heat pump cycle 10b in the single cooling mode, the controller 60 fully opens the heating expansion valve 15a, throttles the cooling expansion valve 15c, fully closes the hot gas flow control valve 15d, and fully closes the outdoor unit pressure control valve 19b. The controller 60 also closes the first on-off valve 23c and opens the second on-off valve 23d.

[0449] For this reason, in the heat pump cycle 10b in the sole cooling mode, the refrigerant discharged from the compressor 11 is switched to a refrigerant circuit in which it circulates in the following order: the muffler section 12, the indoor condenser 14, the heating expansion valve 15a which is in a fully open state, the outdoor heat exchanger 16, the second fixed throttle 25b, the receiver section 24, the cooling expansion valve 15c which is in a throttled state, the chiller 20, and the suction port of the compressor 11.

[0450] In the low-temperature side heat medium circuit 30 in the single cooling mode, the low-temperature side heat medium pumped from the low-temperature side pump 31 circulates in the same manner as in the cooling / air-conditioning mode. In the indoor air-conditioning unit 50 in the single cooling mode, the indoor blower 52 is stopped.

[0451] Therefore, in the heat pump cycle 10 in the single cooling mode, a vapor compression refrigeration cycle is configured in which the outdoor heat exchanger 16 functions as a condenser and the chiller 20 functions as an evaporator.

[0452] In the low-temperature side heat medium circuit 30 in the single cooling mode, the low-temperature side heat medium cooled in the chiller 20 flows through the coolant passage 80a of the battery 80, as in the cooling / air-cooling mode, thereby cooling the battery 80.

[0453] As described above, in the vehicle air conditioner 1b of this embodiment, by switching the operation mode, it is possible to perform comfortable air conditioning for the vehicle interior and appropriate temperature adjustment of the battery 80, which is an on-board device.

[0454] Moreover, the heat pump cycle 10b of the present embodiment employs the thermostatic expansion valve 27. As a result, the amount of heat absorbed in the indoor evaporator 18 can be increased, and the coefficient of performance (COP) of the cycle can be improved.

[0455] Furthermore, in this embodiment, since the compressor module 120 is employed, the same effects as those of the first embodiment can be obtained. That is, the noise of the compressor 11 can be sufficiently suppressed without causing a decrease in productivity of the vehicle air conditioner 1b, which is a heat pump cycle device.

[0456] (Fourth embodiment) In this embodiment, a modified example of the second embodiment will be described. In this embodiment, as shown in the overall configuration diagram of Fig. 11, a cooling passage 22f is formed as an internal refrigerant passage in a flow path box 111 of a compressor module 110. The cooling passage 22f is an internal refrigerant passage that extends from the outlet side of the evaporation pressure regulating valve 19 to one inlet of the fifth internal three-way joint portion 13e.

[0457] 11, the cooling passage 22f is formed so as to flow around the electric devices such as the cooling expansion valve 15b, the cooling expansion valve 15c, and the hot gas flow control valve 15d. Therefore, in the vehicle air conditioner 1a, in an operation mode in which the low-pressure side refrigerant flows through the cooling passage 22f, such as in the single cooling mode, the cooling and cooling mode, the single dehumidification and heating mode, and the cooling and dehumidification and heating mode, the above-mentioned electric devices can be cooled.

[0458] In other words, the cooling expansion valve 15b, the cooling expansion valve 15c, and the hot gas flow rate adjustment valve 15d of this embodiment are arranged so as to be cooled by the cold energy of the low-pressure side refrigerant flowing through the cooling passage 22f.

[0459] Other configurations of the vehicle air conditioner 1a are the same as those of the second embodiment. Therefore, according to the vehicle air conditioner 1a of this embodiment, the same effects as those of the second embodiment can be obtained. That is, the noise of the compressor 11 can be sufficiently suppressed without causing a deterioration in productivity of the vehicle air conditioner 1a, which is a heat pump cycle device.

[0460] Furthermore, in the compressor module 110 of the present embodiment, since the cooling passage 22f is formed, the electric equipment attached to the compressor module 110 can be cooled by the low-pressure side refrigerant of the heat pump cycle 10a. Therefore, the operation of the electric equipment attached to the compressor module 110 can be stabilized.

[0461] In this embodiment, an example in which only the cooling passage 22f is provided has been described, but the cooling passage 22f may be added to the second embodiment. That is, the cooling passage 22f may be provided in parallel with the internal refrigerant passage that directly connects the outlet side of the evaporation pressure regulating valve 19 and one inlet of the fifth internal three-way joint portion 13e. This makes it possible to appropriately adjust the flow rate of the low-pressure side refrigerant flowing through the cooling passage 22f.

[0462] Fifth embodiment In this embodiment, as shown in FIG. 12, an example in which a compressor module 130 is applied to the vehicle air conditioner 1 described in the first embodiment will be described.

[0463] In the compressor module 130 of this embodiment, similarly to the first embodiment, the components of the heat pump cycle 10, such as the compressor 11, the muffler section 12, the heating expansion valve 15a, the cooling expansion valve 15b, the cooling expansion valve 15c, the hot gas flow control valve 15d, the evaporation pressure control valve 19, the chiller 20, the accumulator section 21, the dehumidification opening / closing valve 23a, and the heating opening / closing valve 23b, are integrated together.

[0464] The basic configuration of the compressor module 130 is similar to that of the compressor module 100 described in the first embodiment. As shown in Fig. 13, the compressor module 130 includes a metal flow path box 131. Also, as shown in Fig. 14, the compressor module 130 includes a resin cover member 132. Also, in the heat pump cycle 10 of the present embodiment, the accumulator unit 21 is formed of a separate member from the flow path box 131.

[0465] The flow path box 131 of this embodiment is formed by combining a plurality of metal members. Specifically, the flow path box 131 of this embodiment has a first box member 1311 and a second box member 1312. Both the first box member 1311 and the second box member 1312 are formed of rectangular plate-like members.

[0466] The first box member 1311 forms the bottom surface of the compressor module 130. Among the components of the heat pump cycle 10 described above, the compressor 11 and the accumulator section 21 are integrated by being attached to the first box member 1311. The muffler section 12 is integrally formed with the first box member 1311.

[0467] In addition, the heating expansion valve 15a, the cooling expansion valve 15b, the cooling expansion valve 15c, the hot gas flow control valve 15d, the evaporative pressure control valve 19, the chiller 20, the dehumidification on-off valve 23a, and the heating on-off valve 23b are integrated by being attached to the second box member 1312.

[0468] The first box member 1311 and the second box member 1312 are fixed by means of bolts or the like so that their flat surfaces are perpendicular to each other. More specifically, the first box member 1311 and the second box member 1312 are fixed so that one end face of the second box member 1312 abuts against the flat surface of the first box member 1311.

[0469] At least one of an internal refrigerant passage and an internal heat medium passage is formed inside the first box member 1311 and the second box member 1312. A seal member (not shown) is interposed between the contact surfaces of the first box member 1311 and the second box member 1312. This prevents the refrigerant or low-temperature side heat medium from leaking out from a gap in the contact portion between the first box member 1311 and the second box member 1312.

[0470] The first box member 1311 is formed with a plurality of (four in this embodiment) mounting portions 131t for mounting the compressor module 130 to an object to be mounted (a vehicle in this embodiment). The mounting portions 131t are formed by portions that protrude from an end portion of the first box member 1311 in parallel with the flat surface.

[0471] Each mounting portion 131t has a through hole for passing a bolt therethrough. An annular anti-vibration rubber 131u is disposed along the opening edge of the through hole formed in the mounting portion 131t. The anti-vibration rubber 131u is a vibration-isolating member that suppresses the vibration of the flow path box 131 from being transmitted to the vehicle.

[0472] As in the first embodiment, the cover member 132 is attached to the flow path box 131 to form an accommodation space 133, which is an enclosed space for accommodating the compressor 11 and the like, inside the compressor module 130. The cover member 132 is formed in a box shape with one side of the rectangular parallelepiped being open. Therefore, as shown in Fig. 14, the outer appearance of the compressor module 130 is a rectangular parallelepiped.

[0473] Of the six outer surfaces of the rectangular parallelepiped shape of the compressor module 130, the bottom surface is formed by a first box member 1311 of the flow path box 131. The remaining five surfaces are formed by a cover member 132. For this reason, in the compressor module 130, the second box member 1312 of the flow path box 131 is also disposed within the accommodation space 133.

[0474] As in the first embodiment, insulation material 134 is arranged over almost the entire inner wall surface of the cover member 132 and the surface of the flow path box 131 facing the storage space 133, i.e., the inner surface of the compressor module 130 facing the storage space 133.

[0475] The compressor 11, the heating expansion valve 15a, the cooling expansion valve 15b, the cooling expansion valve 15c, the hot gas flow rate control valve 15d, the evaporation pressure control valve 19, the chiller 20, the accumulator section 21, the dehumidification on-off valve 23a, and the heating on-off valve 23b are accommodated inside the accommodation space 133. For this reason, the compressor side outlet 131a, the compressor side inlet 131b, the chiller side outlet 131i, and the chiller side inlet 131j are formed inside the accommodation space 133.

[0476] More specifically, the compressor side outlet 131a is formed in the accumulator unit 21, which is a component device arranged in the accommodation space 103, and is thereby formed inside the accommodation space 133. Moreover, the compressor side inlet 131b is formed on the inner surface of the flow path box 131 on the accommodation space 103 side, and is thereby formed inside the accommodation space 133.

[0477] Moreover, the indoor condenser 14, the outdoor heat exchanger 16, and the indoor evaporator 18 are external components, similar to the first embodiment.

[0478] Therefore, the condenser side outlet 131c, the condenser side inlet 131d, the outdoor unit side outlet 131e, the outdoor unit side inlet 131f, the evaporator side outlet 131g, and the evaporator side inlet 131h are formed on the outer surface of the flow path box 131, and thereby are formed outside the storage space 133.

[0479] Therefore, in this embodiment, the condenser side outlet 131c, the condenser side inlet 131d, the outdoor unit side outlet 131e, the outdoor unit side inlet 131f, the evaporator side outlet 131g, and the evaporator side inlet 131h are external connection ports to which the inlet and outlet sides of external component equipment are connected.

[0480] In addition, as in the first embodiment, the compressor 11 is fixed to multiple (four in this embodiment) fixing portions 131s formed on the surface forming the storage space 133 of the first box member 1311 via vibration-proof rubber 11c.

[0481] Moreover, the accumulator portion 21 is fixed to a fixing portion formed on a surface of the first box member 1311 that defines the accommodation space 133 by means of screw fastening, press fitting, adhesive, or the like.

[0482] Moreover, the muffler section 12 is formed in the first box member 1311. The muffler section 12 is formed in a shape that bulges toward the accommodation space 133 in order to form a buffer space. The muffler section 12 is disposed in the first box member 1311 so as to be surrounded by a plurality of fixing portions 131s. In other words, the plurality of fixing portions 131s are disposed around the area where the muffler section 12 is formed.

[0483] As a result, in the compressor module 130, the heat of the high-pressure side refrigerant in the muffler section 12 can be transferred to the vibration-proof rubber 11c to heat the vibration-proof rubber 11c. In other words, the vibration-proof rubber 11c is arranged so that it can be heated by the heat of the high-pressure side refrigerant in the muffler section 12. The fixing and electrical connections of the other components are similar to those in the first embodiment.

[0484] Other configurations and operations of the vehicle air conditioner 1 are the same as those of the first embodiment. Therefore, according to the vehicle air conditioner 1 of this embodiment, it is possible to obtain the same effects as those of the first embodiment. That is, the noise of the compressor 11 can be sufficiently suppressed without causing a decrease in productivity of the vehicle air conditioner 1, which is a heat pump cycle device.

[0485] Furthermore, the compressor module 130 of the present embodiment employs a box-shaped cover member 132. With this, by disposing a seal member around the first box member 1311 of the flow path box 131, it is possible to easily make the accommodation space 133 into a sealed space without requiring a seal member of a complex shape.

[0486] Furthermore, in the compressor module 130 of this embodiment, the heat of the high-pressure side refrigerant in the muffler section 12, which is the high-pressure side refrigerant device, can be transferred to the vibration-proof rubber 11c to heat the vibration-proof rubber 11c. This makes it possible to suppress a decrease in the elasticity of the vibration-proof rubber 11c, as in the second embodiment, and effectively suppresses the flow path box 131 and the cover member 132 from generating noise.

[0487] Furthermore, in the compressor module 130 of this embodiment, the heat insulating material 134 is disposed on the inner surface on the side of the accommodation space 133. This makes it possible to prevent the heat insulating material 134 from peeling off or from deteriorating due to exposure to water or the like. When arranging the heat insulating material 134 on the inner surface on the side of the accommodation space 133, it may be arranged by applying it with a spray or the like.

[0488] Moreover, the compressor module 130 of the present embodiment includes a mounting portion 131t on which the vibration-proof rubber 131u is disposed. With this, the vibration-proof rubber 11c interposed between the compressor 11 and the flow path box 131 and the vibration-proof rubber 131u interposed between the flow path box 131 and the vehicle can more effectively achieve the noise reduction effect and the vibration suppression effect of the compressor module 130.

[0489] (Other embodiments) The present invention is not limited to the above-described embodiment, and various modifications can be made as follows without departing from the spirit of the present invention.

[0490] (1) In the above-described embodiment, vehicle air conditioners 1, 1a, and 1b have been described as heat pump cycle devices to which the compressor module of the present invention is applied. However, the heat pump cycle devices to which the compressor module is applied are not limited to vehicle air conditioners.

[0491] For example, the air conditioner may be a stationary air conditioner with a temperature adjustment function that adjusts the temperature of an object to be adjusted (for example, a computer, a computer server device, or other electrical equipment) while performing indoor air conditioning.

[0492] In the above embodiment, an example has been described in which the temperature of the battery 80 is adjusted as an in-vehicle device that is a temperature adjustment target, but the in-vehicle device is not limited to the battery 80. For example, the temperature of an inverter, a PCU, a transaxle, a control device for ADAS, etc. may be adjusted.

[0493] The inverter supplies power to the motor generator, etc. The PCU is a power control unit that transforms electricity and distributes power. The transaxle is a power transmission mechanism that integrates the transmission, differential gear, etc. The control device for ADAS is a control device for advanced driver assistance systems.

[0494] (2) The specific configurations of the compressor modules 100, 110, 120, and 130 according to the present invention are not limited to those disclosed in the above-described embodiments.

[0495] For example, the components of the heat pump cycle apparatuses 1, 1a, 1b integrated into the compressor modules 100-130 are not limited to those disclosed in the above-mentioned embodiments. As long as the compressor 11 is accommodated in at least the accommodation spaces 103, 113, 123, 133, the other components may or may not be integrated. Furthermore, the other components integrated into the compressor modules 100-130 may be disposed inside or outside the accommodation spaces 103-133.

[0496] Furthermore, as described in the above-mentioned embodiment, the compressor side outlets 101a, 111a, 121a, 131a and the compressor side inlets 101b, 111b, 121b, 131b may be formed on the inner surfaces of the flow path boxes 101, 111, 121, 131, and thereby may be formed inside the storage spaces 103-133.

[0497] Alternatively, the compressor side outlets 101a-131a and the compressor side inlets 101b-131b may be formed inside the storage spaces 103-133 by being formed in the components of the heat pump cycle devices 1, 1a, 1b arranged inside the storage spaces 103-133.

[0498] Similarly, the outer connection ports 101c-131h may be formed on the outer surfaces of the flow path boxes 101-131, and thereby may be formed outside the storage spaces 103-133. Furthermore, the outer connection ports 101c-131h may be formed on the components of the heat pump cycle apparatuses 1, 1a, and 1b attached to the flow path boxes 101-131, and thereby may be formed outside the storage spaces 103-133.

[0499] The arrangement of the anti-vibration rubber 11c is not limited to the example disclosed in the above embodiment. For example, the anti-vibration rubber 11c may be arranged so as to be heated by the high-pressure side refrigerant in the receiver 24 described in the third embodiment.

[0500] In the above-described embodiment, an example has been described in which an aluminum alloy is used as the material for forming the flow path boxes 101-131, but the material for the flow path boxes 101-131 is not limited to an aluminum alloy. If iron or a stainless steel alloy, which has a higher specific gravity than aluminum, is used, the weight of the compressor modules 100-130 as a whole can be increased, and the vibration resistance of the compressor modules can be improved.

[0501] Furthermore, although an example has been described in which polypropylene is used as the material for the cover members 102, 122, and 132, the material for the cover members 102-132 may be other types of resin, or may be the same metal as that for the flow path boxes 101-131. Regardless of which material is used for the flow path boxes 101-131 and the cover members 102-132, it is desirable that the accommodation spaces 103-133 can be formed as sealed spaces.

[0502] The heat insulating materials 104, 124, 134 may be disposed on the outer surfaces of the compressor modules 100-120 as in the first to fourth embodiments, or may be disposed on the inner surface of the compressor module 130 as in the fifth embodiment. Furthermore, heat insulating portions may be disposed on both the outer surface and the inner surface of the compressor module.

[0503] Moreover, an internal refrigerant passage similar to the cooling passage 22f described in the fourth embodiment may be formed in the flow path boxes 101, 121, and 131. Moreover, the attachment portion 131t in which the vibration isolating rubber 131u described in the fifth embodiment is arranged may be formed in the compressor modules 100, 110, and 120. Furthermore, the attachment portion 131t is not limited to the flow path boxes 101-131, and may be formed in the cover members 102-132.

[0504] (3) The specific configuration of the heat pump cycle apparatus to which the compressor module according to the present invention is applied is not limited to the configuration disclosed in the above embodiment.

[0505] For example, the evaporation pressure regulating valve 19 is not limited to an electric variable throttle mechanism. A mechanical variable throttle mechanism that increases the valve opening degree in accordance with an increase in the pressure of the refrigerant on the outlet side of the indoor evaporator 18 may be used as the evaporation pressure regulating valve.

[0506] For example, the refrigerant of the heat pump cycles 10, 10a, and 10b is not limited to R1234yf. The refrigerant may be R134a, R600a, R410A, R404A, R32, R407C, or the like. Alternatively, a mixed refrigerant obtained by mixing a plurality of these refrigerants may be used.

[0507] For example, the low-temperature heat medium of the low-temperature heat medium circuits 30 and 30a and the high-temperature heat medium of the high-temperature heat medium circuit 40 are not limited to an ethylene glycol aqueous solution. As the low-temperature heat medium and the high-temperature heat medium, dimethylpolysiloxane, a solution containing nanofluid, antifreeze, an aqueous liquid refrigerant containing alcohol, or a liquid medium containing oil may be used.

[0508] (4) The operating mode of the heat pump cycle apparatus to which the compressor module according to the present invention is applied is not limited to the mode disclosed in the above embodiment.

[0509] For example, in the vehicle air conditioner 1 described in the first embodiment, an outside air heat absorption hot gas heating mode may be executed.

[0510] In the heat pump cycle 10 in the outdoor air heat absorption hot gas heating mode, the controller 60 throttles the heating expansion valve 15a, fully closes the cooling expansion valve 15b, fully opens the cooling expansion valve 15c, and throttles the hot gas flow control valve 15d. The controller 60 also closes the dehumidification opening / closing valve 23a and the heating opening / closing valve 23b.

[0511] For this reason, in the heat pump cycle 10a in the single heating mode, the refrigerant discharged from the compressor 11 circulates in the order of the muffler section 12, the indoor condenser 14, the heating expansion valve 15a in the throttled state, the outdoor heat exchanger 16, the cooling expansion valve 15c in the fully open state, the chiller 20, the accumulator section 21, and the suction port of the compressor 11. At the same time, the refrigerant discharged from the compressor 11 is switched to a refrigerant circuit in which the refrigerant circulates in the order of the muffler section 12, the hot gas flow control valve 15d of the hot gas passage 22a in the throttled state, the chiller 20, the accumulator section 21, and the suction port of the compressor 11.

[0512] In addition, in the low-temperature side heat medium circuit 30 in the outside air heat absorption hot gas heating mode, the low-temperature side pump 31 is stopped.

[0513] Therefore, in the heat pump cycle 10 in the outdoor air heat absorption hot gas heating mode, the flow of the refrigerant discharged from the compressor 11 is branched at the first inner three-way joint portion 13a.

[0514] One of the refrigerant branches at the first internal three-way joint portion 13a flows into the indoor condenser 14 and dissipates heat to the blown air. This heats the blown air. The refrigerant that flows out of the indoor condenser 14 flows into the heating expansion valve 15a and is reduced in pressure. The refrigerant reduced in pressure by the heating expansion valve 15a flows into the outdoor heat exchanger 16. The refrigerant that flows into the outdoor heat exchanger 16 absorbs heat from the outside air and evaporates. The refrigerant that flows out of the outdoor heat exchanger 16 flows into the chiller 20.

[0515] On the other hand, the other refrigerant branched at the first internal three-way joint 13a is depressurized by adjusting the flow rate at the hot gas flow rate control valve 15d. The refrigerant with a relatively high enthalpy depressurized at the hot gas flow rate control valve 15d flows into the chiller 20 via the fourth internal three-way joint 13d.

[0516] In the chiller 20, the refrigerant decompressed by the cooling expansion valve 15c and the refrigerant decompressed by the hot gas flow rate control valve 15d are mixed. At this time, since the low-temperature side pump 31 is stopped, there is no heat exchange between the refrigerant and the low-temperature side heat medium in the chiller 20. The refrigerant flowing out of the chiller 20 flows into the accumulator section 21 and is separated into gas and liquid. The gas-phase refrigerant separated in the accumulator section 21 is sucked into the compressor 11 and compressed again.

[0517] In the interior air conditioning unit 50 in the outside air heat absorption hot gas heating mode, the ventilation air blown from the interior blower 52 passes through the interior evaporator 18. The ventilation air that has passed through the interior evaporator 18 is heated by the interior condenser 14 according to the opening degree of the air mix door 54. Then, the ventilation air heated by the interior condenser 14 is blown into the vehicle interior, thereby heating the vehicle interior.

[0518] In the outside air heat absorption hot gas heating mode, the hot gas flow rate adjustment valve 15d is in a throttled state, so that a refrigerant with a relatively high enthalpy can be caused to flow into the chiller 20 via the fourth inner three-way joint portion 13d.

[0519] Therefore, in the vehicle air conditioner 1 in the parallel dehumidification hot gas heating mode, even if the refrigerant discharge capacity of the compressor 11 is increased compared to the parallel dehumidification heating mode, the suction side refrigerant flowing out to the suction port side of the compressor 11 can be a gas phase refrigerant having a degree of superheat. Furthermore, by increasing the compression work of the compressor 11, the amount of heat dissipated from the refrigerant in the interior condenser 14 to the blown air can be increased, thereby improving the heating capacity.

[0520] The compressor module according to the present invention is effective for suppressing noise in a heat pump cycle device having an operation mode that increases the refrigerant discharge capacity of the compressor 11, such as an outdoor air heat absorption hot gas heating mode.

[0521] In the above-described vehicle air conditioners 1, 1a, 1b, a warm-up mode may be executed in which some of the components and the refrigerant are heated when the outside air temperature is extremely low (for example, when the outside air temperature Tam is −10° C. or lower).

[0522] In the warm-up mode, the control device 60 fully closes the heating expansion valve 15a, the cooling expansion valve 15b, the cooling expansion valve 15c, and the hot gas flow control valve 15d. Furthermore, the control device 60 closes the dehumidification opening / closing valve 23a, the heating opening / closing valve 23b, the first opening / closing valve 23c, and the second opening / closing valve 23d.

[0523] Therefore, in the heat pump cycles 10, 10a, and 10b in the warm-up mode, the refrigerant discharged from the compressor 11 is switched to a refrigerant circuit in which it circulates in the order of the hot gas flow rate control valve 15d in the hot gas passage 22a, the chiller 20, and the suction port side of the compressor 11. This makes it possible to heat and warm up some of the components and the refrigerant whose temperatures have dropped during extremely low outside air temperatures. [Explanation of symbols]

[0524] 1, 1a, 1b...vehicle air conditioning device (heat pump cycle device), 11...compressor, 14...indoor condenser (external component), 16... outdoor heat exchanger (external component equipment), 18... indoor evaporator (external component equipment), 100, 110, 120, 130...Compressor module, 101, 111, 121, 131...flow path box (passage forming member), 102, 122, 132 ... cover member, 103, 113, 123, 133 ... storage space, 101a, 111a, 121a, 131a...Compressor side outlet, 101b, 111b, 121b, 131b...Compressor side inlet, 101c~131h…Outside connection port

Claims

1. A compressor module applied to a heat pump cycle device (1, 1a, 1b), A compressor (11) that draws in a refrigerant, compresses it, and discharges it; A passage forming member (101, 111, 121, 131) having a plurality of internal refrigerant passages formed therein through which the refrigerant flows; a cover member (102, 122, 132) that, together with the passage forming member, forms an accommodation space (103, 113, 123, 133) that accommodates the compressor, A compressor side inlet (101b, 111b, 121b, 131b) and a compressor side outlet (101a, 111a, 121a, 131a) communicating with the internal refrigerant passage are formed inside the accommodation space, Outside the storage space, outer connection ports (101c to 101h, 111g, 111h, 121c to 121h, 131c to 131h) communicating with the internal refrigerant passage are formed, The compressor-side inlet is connected to a discharge port side of the compressor, The compressor-side outlet is connected to a suction port side of the compressor, The outer connection port is connected to an inlet / outlet side of an external component device (14, 16, 18) that is arranged outside the storage space among the components of the heat pump cycle device, A compressor module having at least a portion of an outer surface defined by both the passage forming member and the cover member.

2. A compressor module applied to a heat pump cycle device (1, 1a, 1b), A compressor (11) that draws in a refrigerant, compresses it, and discharges it; A passage forming member (101, 111, 121, 131) having a plurality of internal refrigerant passages formed therein through which the refrigerant flows; a cover member (102, 122, 132) that, together with the passage forming member, forms an accommodation space (103, 113, 123, 133) that accommodates the compressor, A compressor side inlet (101b, 111b, 121b, 131b) and a compressor side outlet (101a, 111a, 121a, 131a) communicating with the internal refrigerant passage are formed inside the accommodation space, Outside the storage space, outer connection ports (101c to 101h, 111g, 111h, 121c to 121h, 131c to 131h) communicating with the internal refrigerant passage are formed, The compressor-side inlet is connected to a discharge port side of the compressor, The compressor-side outlet is connected to a suction port side of the compressor, The outer connection port is connected to an inlet / outlet side of an external component device (14, 16, 18) that is arranged outside the storage space among the components of the heat pump cycle device, The compressor is fixed to the passage forming member via a vibration isolating member (11c), The passage forming member has a portion that forms a high-pressure side refrigerant device (12, 141, 24) into which a high-pressure side refrigerant of the heat pump cycle device flows, among the components of the heat pump cycle device, The vibration-proof member has thermoplastic properties and is disposed in the high-pressure-side refrigerant equipment so as to be heatable by the high-pressure-side refrigerant.

3. A compressor module as described in claim 2, wherein the vibration-damping member has thermoplastic properties and is arranged so that it can be heated by heat generated by the compressor.

4. A compressor module applied to a heat pump cycle device (1, 1a, 1b), A compressor (11) that draws in a refrigerant, compresses it, and discharges it; A passage forming member (101, 111, 121, 131) having a plurality of internal refrigerant passages formed therein through which the refrigerant flows; a cover member (102, 122, 132) that, together with the passage forming member, forms an accommodation space (103, 113, 123, 133) that accommodates the compressor, A compressor side inlet (101b, 111b, 121b, 131b) and a compressor side outlet (101a, 111a, 121a, 131a) communicating with the internal refrigerant passage are formed inside the accommodation space, Outside the storage space, outer connection ports (101c to 101h, 111g, 111h, 121c to 121h, 131c to 131h) communicating with the internal refrigerant passage are formed, The compressor-side inlet is connected to a discharge port side of the compressor, The compressor-side outlet is connected to a suction port side of the compressor, The outer connection port is connected to an inlet / outlet side of an external component device (14, 16, 18) that is arranged outside the storage space among the components of the heat pump cycle device, The compressor is fixed to the passage forming member via a vibration isolating member (11c), The vibration-proof member has thermoplastic properties and is arranged in a compressor module so as to be heatable by heat generated by the compressor.

5. 5. The compressor module according to claim 1, wherein the accommodation space is formed as a sealed space.

6. A low-pressure hose (11a) connecting the compressor side outlet and the suction port; a high-pressure hose (11b) connecting the discharge port and the compressor-side inlet, The compressor module according to any one of claims 1 to 5, wherein the low pressure hose (11a) and the high pressure hose (11b) are flexible and are attached to the compressor and the passage forming member in a curved state.

7. An electric device (15a to 15d, 19, 19b, 23a to 23d) that is operated by electricity is fixed to the passage forming member, 7. The compressor module according to claim 1, wherein the electric device is arranged so as to be cooled by a low-pressure side refrigerant of the heat pump cycle device flowing through the internal refrigerant passage.

8. 8. The compressor module according to claim 1, further comprising a heat insulating portion (104, 124, 134) for suppressing heat transfer between the air inside the accommodation space and the air outside the accommodation space.

9. The heat pump cycle device has a discharge-side branching section (13a) that branches the flow of the refrigerant discharged from the compressor, and a heating section that heats a fluid to be heated using one of the refrigerants branched at the discharge-side branching section as a heat source, 9. The compressor module according to claim 1, wherein, during an operation mode for heating the fluid to be heated, the refrigerant flowing out of the heating section and the other refrigerant branched at the discharge side branch section are joined together and sucked into the compressor.

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