Connecting Devices

Abstract

To provide a connection device capable of suppressing pressure loss.SOLUTION: A connection device for connecting at least one inflow pipe to at least one outflow pipe in a refrigeration cycle device in which refrigerant circulates, includes a casing 110, upstream side flow path parts 120, 130 for allowing the flow of refrigerant to the inside of the casing, a downstream side flow path part 140 for allowing the flow of the refrigerant flowing into the casing to the outside of the casing, and either combination parts 141, 142 for combining the refrigerant flowing from the plurality of upstream side flow path parts with the downstream side flow path part or a branch part for branching the refrigerant flowing from the upstream side flow path parts into the plurality of downstream side flow path parts. If it has the combination part, at least one of the plurality of upstream side flow path parts extends deviating an angle larger than 0° and smaller than 90°from the downstream direction. If it has the branch part, at least one of the plurality of downstream side flow path parts extends so as to deviate an angle larger than 0°and smaller than 90°from the upstream direction.SELECTED DRAWING: Figure 3

Description

[Technical field]

[0001] The present disclosure relates to a connection device. [Background technology]

[0002] 2. Description of the Related Art Conventionally, a connection device is known that connects a plurality of components that constitute a refrigerant circulation cycle in which a refrigerant circulates so that they communicate with each other (see, for example, Patent Document 1). [Prior art documents] [Patent documents]

[0003] [Patent Document 1] JP 2014-31998 A Summary of the Invention [Problem to be solved by the invention]

[0004] The connection device described in Patent Document 1 has a structure for communicating refrigerant pipes that are in a positional relationship in three directions with each other. Specifically, the connection device described in Patent Document 1 is T-shaped, and has joints at both ends to which the refrigerant pipes are connected, and also has joints at positions perpendicular to the joints at both ends to which the refrigerant pipes are connected.

[0005] In a connection device configured in this way, for example, when the inlet pipe for introducing the refrigerant is connected to the joints at both ends and the outlet pipe for discharging the refrigerant is connected to the remaining joint, the refrigerant flowing in from the joints at both ends joins and collides, and the flow direction of the refrigerant is bent by 90 degrees. Such collisions of the refrigerant and changes in the flow direction of the refrigerant are factors that cause pressure loss, so it is desirable to suppress them.

[0006] An object of the present disclosure is to provide a connection device capable of suppressing pressure loss. [Means for solving the problem]

[0007] The invention described in claim 1 is In a refrigeration cycle device (10) in which a refrigerant circulates, multiple Inlet piping (11a, 11b, 11d, 11e) and 1 Connect the two outlet pipes (11c) to Multiple The refrigerant flowing in from the inlet pipe Multiple A connection device that leads to an outflow pipe provided downstream of the inflow pipe in the refrigerant flow, A housing (110, 210, 310), Multiple The inlet pipe is connected to the inlet pipe one-to-one, and allows the refrigerant to flow into the housing. Multiple Upstream flow path section (120, 130, 220, 230, 240, 320, 33 0) and, Connected one-to-one to the outflow pipe, Multiple A downstream side flow passage portion (140, 250, 350) is connected to the upstream side flow passage portion and causes the refrigerant that has flowed into the inside of the housing to flow out to the outside of the housing. 0) and, A merging section (141, 142, 251, 252, 351) that merges the refrigerant flowing from the multiple upstream flow passage sections into a downstream flow passage section )and , If When the direction in which the downstream side flow passage portion extends from the upstream portion toward the refrigerant flow downstream side of the downstream side flow passage portion is defined as the downstream direction, The part , the first inclined upstream flow path section (120) extending along a direction offset from the downstream direction by an angle greater than 0° and less than 90°, and a second inclined upstream flow path section (130) extending along a direction different from the direction in which the first inclined upstream flow path section extends, the second inclined upstream flow path section (130) extending along a direction offset from the downstream direction by an angle greater than 0° and less than 90°, The refrigeration cycle device is applied to an air conditioning device for a vehicle, and includes a compressor (12) that compresses and discharges a sucked refrigerant, a heating section (13, 30) that uses the refrigerant discharged from the compressor as a heat source to heat air to be blown to a space to be air-conditioned, an air-conditioning heat exchanger (14) that evaporates the refrigerant flowing out of the heating section to cool the blown air before it is heated by the heating section, and a cooling section (16, 40) that evaporates the refrigerant flowing out of the heating section to cool an object to be cooled other than the blown air, The plurality of inlet pipes include an air conditioning inlet pipe (11a) through which the refrigerant flowing out from the air conditioning heat exchanger flows, and a cooling section inlet pipe (11b) through which the refrigerant flowing out from the cooling section flows, The outlet pipe is a compressor outlet pipe (11c) that introduces a refrigerant to the compressor, The first inclined upstream flow passage portion is connected to the air conditioning inlet pipe, The second inclined upstream flow passage portion is connected to the cooling section inlet pipe, The downstream flow passage portion is connected to a compressor outflow pipe, The first inclined upstream channel section has a smaller extension in the downstream direction than the second inclined upstream channel section. Connection device.

[0008] According to this, when the connection device is configured to merge the refrigerant internally, pressure loss caused when the flow direction of the refrigerant changes when merging from the upstream flow path section to the downstream flow path section can be suppressed, compared to a configuration in which the upstream flow path section extends at an angle of 90° from a predetermined merging reference direction.

[0009] In contrast, when the connection device is configured to branch the refrigerant internally, pressure loss can be reduced when the flow direction of the refrigerant that flows in from the upstream flow path section changes as it branches, compared to a configuration in which the downstream flow path section extends at an angle of 90° from a predetermined branching reference direction.

[0010] The reference symbols in parentheses attached to each component indicate an example of the correspondence between the component and specific components described in the embodiments described below. [Brief description of the drawings]

[0011] [Figure 1] 1 is a schematic configuration diagram of a vehicle air conditioning device according to a first embodiment. [Diagram 2] 1 is a block diagram showing a control device for a vehicle air conditioner according to a first embodiment; [Diagram 3] 1 is a perspective view of a connection device according to a first embodiment. FIG. [Figure 4] FIG. 4 is a cross-sectional view taken along line IV-IV of FIG. [Diagram 5] FIG. 2 is a diagram showing the positional relationship between a connection device and a compressor according to the first embodiment. [Figure 6] FIG. 4 is a relationship diagram showing the relationship between the pressure loss of the connection device according to the first embodiment, the manufacturing cost of the connection device, and the diameter ratio of the connection portion. [Figure 7] 4 is a diagram showing a flow direction of a refrigerant when the refrigerant flows in from a steep upward flow path portion of the connection device according to the first embodiment. FIG. [Figure 8] 4 is a diagram showing a flow direction of a refrigerant when the refrigerant flows in from a lower upstream flow path portion of the connection device according to the first embodiment. FIG. [Figure 9] 4A to 4C are diagrams illustrating the flow directions of a refrigerant when the refrigerant flows in from a steep upward flow path section and a low upward flow path section of the connection device according to the first embodiment. [Figure 10] FIG. 2 is a perspective view of a first comparative connecting device. [Figure 11] FIG. 13 is a perspective view of a second comparative connecting device. [Figure 12] FIG. 11 is a perspective view of a connection device according to a second embodiment. [Figure 13] FIG. 13 is a cross-sectional view taken along line XIII-XIII of FIG. [Figure 14] 13 is a diagram showing the flow direction of a coolant flowing inside a housing of the connection device according to the second embodiment. FIG. [Figure 15] FIG. 11 is a schematic configuration diagram of a vehicle air conditioner according to a third embodiment. [Figure 16] FIG. 11 is a perspective view of a connection device according to a third embodiment. [Figure 17] 17 is a cross-sectional view taken along line XVII-XVII of FIG. 16. [Figure 18] 13 is a diagram showing the flow direction of a coolant flowing inside a housing of a connection device according to a third embodiment. FIG. [Figure 19] FIG. 13 is a cross-sectional view of a connection device according to a third modified example of the third embodiment. [Figure 20] FIG. 13 is a cross-sectional view of a connection device according to a fourth modified example of the third embodiment. [Figure 21] FIG. 13 is a perspective view of a connection device according to a fourth embodiment. [Figure 22] FIG. 11 is a cross-sectional view of a connection device according to another embodiment. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0012] Hereinafter, the embodiments of the present disclosure will be described with reference to the drawings. In the following embodiments, the same reference numerals are used for parts that are the same as or equivalent to those described in the preceding embodiments, and the description thereof may be omitted. In addition, in the embodiments, when only a part of the components is described, the components described in the preceding embodiments can be applied to the other parts of the components. In the following embodiments, each embodiment can be partially combined with each other, even if not specifically stated, as long as it does not cause any trouble in combination.

[0013] (First embodiment) This embodiment will be described with reference to Figs. 1 to 11. In this embodiment, a connection device 100 according to the present invention is applied to a vehicle air conditioner 1 mounted on an electric vehicle that obtains driving force for traveling from a motor generator 62 described below. This vehicle air conditioner 1 not only heats and cools the blown air to be blown into the vehicle cabin, which is the space to be air-conditioned, but also has a function of cooling a battery 60 that supplies power to an electric motor and the like. Therefore, the object to be cooled in the refrigeration cycle device 10 of this embodiment, which is different from the blown air, is the battery 60.

[0014] As shown in FIG. 1, the vehicle air conditioner 1 includes a refrigeration cycle device 10, a high-temperature side heat medium circuit 30, a low-temperature side heat medium circuit 40, an interior air conditioning unit 50, and the like.

[0015] The refrigeration cycle device 10 is configured to be switchable between refrigerant circuits for various operation modes in order to perform air conditioning in the vehicle cabin. Specifically, the refrigeration cycle device 10 is configured to be switchable between a refrigerant circuit for a cooling mode, a refrigerant circuit for a dehumidification heating mode, a refrigerant circuit for a heating mode, etc., as a refrigerant circuit for an air conditioning operation mode. In addition, the refrigeration cycle device 10 is configured to be switchable between a refrigerant circuit that cools the battery 60 and a refrigerant circuit that does not cool the battery 60 in each air conditioning operation mode. Furthermore, the refrigeration cycle device 10 is configured to be switchable to a refrigerant circuit for a cooling mode that does not perform air conditioning and cools the battery 60.

[0016] The refrigeration cycle device 10 employs an HFO refrigerant (specifically, R1234yf) as a refrigerant, and configures a vapor compression subcritical refrigeration cycle in which the pressure of the refrigerant discharged from the compressor 12 does not exceed the critical pressure of the refrigerant. The refrigeration cycle device 10 is a heat pump cycle.

[0017] Furthermore, the refrigerant is mixed with oil (i.e., refrigeration oil) for lubricating the compressor 12. For example, polyalkylene glycol oil (i.e., PAG oil) that is compatible with the liquid refrigerant is used as the oil. A portion of the oil circulates in the cycle together with the refrigerant.

[0018] As shown in Fig. 1, the refrigeration cycle device 10 has a refrigerant circulation passage 11 for flowing a refrigerant. The refrigerant circulation passage 11 is provided with a compressor 12 for compressing the refrigerant, a water-refrigerant heat exchanger 13 for exchanging heat between the refrigerant and a heat medium, an indoor evaporator 14, a chiller 16, an evaporation pressure control valve 15 for controlling the pressure of the refrigerant, a first expansion valve 17a, and a second expansion valve 17b. The refrigerant circulation passage 11 is also provided with a refrigerant branching section 18 for branching the flow of the refrigerant into a plurality of refrigerant passages, and a connection device 100 for joining the refrigerant flowing from the plurality of refrigerant passages and flowing the refrigerant into a downstream refrigerant passage. The refrigerant circulation passage 11 is further provided with a first refrigerant temperature sensor 19a to a third refrigerant temperature sensor 19c for detecting the temperature of the refrigerant flowing through the refrigerant circulation passage 11, and a first refrigerant pressure sensor 19d to a third refrigerant pressure sensor 19f for detecting the pressure of the refrigerant flowing through the refrigerant circulation passage 11.

[0019] The compressor 12 draws in, compresses, and discharges refrigerant in the refrigeration cycle device 10. The compressor 12 is disposed in a drive unit compartment that is disposed at the front of the vehicle interior and that houses an electric motor and the like. The drive unit compartment forms a space in which at least some of the devices (e.g., a motor generator 62 described later) used to generate or adjust the driving force for running the vehicle are disposed.

[0020] The compressor 12 is an electric compressor in which a fixed-capacity compression mechanism with a fixed discharge capacity is rotationally driven by an electric motor. The rotation speed (i.e., refrigerant discharge capacity) of the compressor 12 is controlled by a control signal output from a control device 70 described later. The discharge port of the compressor 12 is connected to the inlet side of a refrigerant passage of the water-refrigerant heat exchanger 13.

[0021] Further, a first refrigerant temperature sensor 19a for detecting the temperature of the refrigerant discharged from the compressor 12 and a first refrigerant pressure sensor 19d for detecting the pressure of the refrigerant discharged from the compressor 12 are provided in the refrigerant circulation passage 11 on the discharge port side of the compressor 12. The first refrigerant temperature sensor 19a detects an abnormal temperature when the refrigerant discharged from the compressor 12 is at an abnormal temperature, and is provided to protect the compressor 12. The first refrigerant pressure sensor 19d detects an abnormal pressure when the refrigerant discharged from the compressor 12 is at an abnormal pressure, and is provided to protect the compressor 12.

[0022] The first refrigerant temperature sensor 19a transmits a detection signal corresponding to the temperature of the refrigerant discharged from the compressor 12 to the control device 70. The first refrigerant pressure sensor 19d transmits a detection signal corresponding to the pressure of the refrigerant discharged from the compressor 12 to the control device 70.

[0023] The water-refrigerant heat exchanger 13 is a heating heat exchanger that exchanges heat between the high-pressure refrigerant discharged from the compressor 12 and the high-temperature side heat medium circulating in the high-temperature side heat medium circuit 30 to heat the high-temperature side heat medium. The water-refrigerant heat exchanger 13 has a refrigerant passage through which the high-pressure refrigerant discharged from the compressor 12 flows, and a water passage through which the high-temperature side heat medium circulating in the high-temperature side heat medium circuit 30 flows. The water-refrigerant heat exchanger 13 of this embodiment employs a so-called subcooling type heat exchanger. For this reason, the refrigerant passage of the water-refrigerant heat exchanger 13 is provided with a condensation section 13a, a receiver section 13b, and a supercooling section 13c.

[0024] The condensing section 13a is a heat exchange section for condensing the high-pressure refrigerant by exchanging heat between the high-pressure refrigerant discharged from the compressor 12 and the high-temperature heat medium circulating in the high-temperature heat medium circuit 30. The receiver section 13b is a liquid-receiving section that separates the refrigerant flowing out from the condensing section 13a into gas and liquid and stores the separated liquid-phase refrigerant. The supercooling section 13c 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 13b and the high-temperature heat medium. The outlet of the refrigerant passage of the water-refrigerant heat exchanger 13 is connected to the inlet side of a refrigerant branching section 18 having three inlet and outlets that communicate with each other.

[0025] The refrigerant branching section 18 is a three-way joint that has one inlet and two outlets and allows the refrigerant flowing in from the one inlet to flow out from one and the other outlets. The refrigerant branching section 18 may be formed by joining multiple pipes or by providing multiple refrigerant passages in a metal block or a resin block.

[0026] An inlet side of a first expansion valve 17a is connected to one outlet of the refrigerant branching portion 18. An inlet side of a second expansion valve 17b is connected to the other outlet of the refrigerant branching portion 18.

[0027] The first expansion valve 17a is a cooling pressure reducing section that reduces the pressure of the high-pressure refrigerant flowing out from the refrigerant passage of the water-refrigerant heat exchanger 13 and adjusts the flow rate (i.e., mass flow rate) of the refrigerant flowing out downstream at least during an operation mode for cooling the vehicle cabin. The first expansion valve 17a is an electric variable throttling mechanism including a valve body configured to be able to change the throttling opening degree and an electric actuator that changes the opening degree of the valve body.

[0028] The first expansion valve 17a of this embodiment is configured to be able to change the throttle opening in the range of 0 to 100% by adjusting the opening area of ​​the valve body. That is, the first expansion valve 17a has a full opening function that functions as a simple refrigerant passage without exerting almost no flow rate adjustment action or refrigerant pressure reduction action by fully opening the valve (i.e., throttle opening is 100%). In addition, the first expansion valve 17a has a full closing function that closes the refrigerant passage by fully closing the valve opening (i.e., throttle opening is 0%). The outlet of the first expansion valve 17a is connected to the refrigerant inlet side of the indoor evaporator 14.

[0029] The second expansion valve 17b is a heating pressure reducing section that reduces the pressure of the refrigerant flowing out from the refrigerant passage of the water-refrigerant heat exchanger 13 and adjusts the flow rate of the refrigerant flowing out downstream at least during an operation mode in which the vehicle interior is heated. The second expansion valve 17b has a basic configuration similar to that of the first expansion valve 17a. The outlet of the second expansion valve 17b is connected to the inlet side of the refrigerant passage of the chiller 16.

[0030] The first expansion valve 17a and the second expansion valve 17b can switch the refrigerant circuit for each operation mode by the fully open function and the fully closed function. Therefore, the first expansion valve 17a and the second expansion valve 17b also function as a refrigerant circuit switching unit. The operation of the first expansion valve 17a and the second expansion valve 17b is controlled by a control signal (i.e., a control pulse) output from the control device 70.

[0031] The indoor evaporator 14 is a cooling heat exchanger that exchanges heat between the low-pressure refrigerant decompressed in the first expansion valve 17a and the air blown from a blower 53 described later to evaporate the low-pressure refrigerant and cools the air by making the low-pressure refrigerant absorb heat. The indoor evaporator 14 is disposed in an air conditioning case 51 of an indoor air conditioning unit 50 described later. An air conditioning inflow pipe 11a that guides the refrigerant flowing out from the indoor evaporator 14 to the connection device 100 is connected to a refrigerant outlet of the indoor evaporator 14. In this embodiment, the indoor evaporator 14 functions as an air conditioning heat exchanger.

[0032] The air conditioning inlet pipe 11a forms a refrigerant passage through which the refrigerant flows, and is connected at its upstream side in the refrigerant flow to the indoor evaporator 14 and at its downstream side in the refrigerant flow to the connection device 100. The air conditioning inlet pipe 11a is an inlet pipe that allows the refrigerant to flow into the connection device 100.

[0033] The air conditioning inlet pipe 11a is configured to have a size that allows it to be inserted into the refrigerant outlet of the indoor evaporator 14 and the refrigerant inlet of the connection device 100. Specifically, in this embodiment, the air conditioning inlet pipe 11a is a refrigerant pipe with an outer diameter of 15.88 mm from the inlet side to the outlet side. In contrast, the inner diameter of the refrigerant outlet of the indoor evaporator 14 and the inner diameter of a rapid flow inlet 121, which will be described later and through which the refrigerant flows into the connection device 100, are formed slightly larger than 15.88 mm.

[0034] The air conditioning inlet pipe 11a may be a refrigerant pipe having an outer diameter from the inlet side to the outlet side different from 15.88 mm. In this case, the refrigeration cycle device 10 may be configured such that a refrigerant pipe conversion member having an outer diameter on the inlet side and an outer diameter on the outlet side different from each other is attached to the indoor evaporator 14 and the connection device 100, and the air conditioning inlet pipe 11a is connected to the indoor evaporator 14 and the connection device 100.

[0035] Furthermore, the air conditioning inlet pipe 11a is provided with a second refrigerant temperature sensor 19b that detects the temperature of the refrigerant flowing out from the indoor evaporator 14, and a second refrigerant pressure sensor 19e that detects the pressure of the refrigerant flowing out from the indoor evaporator 14. Furthermore, the air conditioning inlet pipe 11a is provided with an evaporation pressure regulating valve 15 that adjusts the pressure of the refrigerant flowing out from the indoor evaporator 14.

[0036] The second refrigerant temperature sensor 19b transmits a detection signal corresponding to the temperature of the refrigerant flowing out from the indoor evaporator 14 to the control device 70. The second refrigerant pressure sensor 19e transmits a detection signal corresponding to the pressure of the refrigerant flowing out from the indoor evaporator 14 to the control device 70.

[0037] The evaporation pressure regulating valve 15 serves to maintain the refrigerant evaporation pressure in the indoor evaporator 14 at or above a predetermined reference pressure in order to suppress frost formation on the indoor evaporator 14. The evaporation pressure regulating valve 15 is configured with a mechanical variable throttle mechanism that increases the valve opening degree as the pressure of the refrigerant on the outlet side of the indoor evaporator 14 increases. In this way, the evaporation pressure regulating valve 15 maintains the temperature at which the refrigerant in the indoor evaporator 14 evaporates at or above a frost suppression temperature (e.g., 1°C) that can suppress frost formation on the indoor evaporator 14.

[0038] The chiller 16 is an evaporation section that performs heat exchange between the low-pressure refrigerant decompressed in the second expansion valve 17b and the low-temperature side heat medium circulating in the low-temperature side heat medium circuit 40, and evaporates the low-pressure refrigerant to exert a heat absorption effect. The chiller 16 has a refrigerant passage through which the low-pressure refrigerant flowing out from the second expansion valve 17b flows, and a water passage through which the low-temperature side heat medium circulating in the low-temperature side heat medium circuit 40 flows. At the outlet of the refrigerant passage of the chiller 16, a cooling section inlet pipe 11b that guides the refrigerant flowing out from the chiller 16 to the connection device 100 is inserted.

[0039] The cooling unit inlet pipe 11b forms a refrigerant passage through which the refrigerant flows, and is connected at its upstream side of the refrigerant flow to the chiller 16 and at its downstream side of the refrigerant flow to the connection device 100. The cooling unit inlet pipe 11b is an inlet pipe that allows the refrigerant to flow into the connection device 100.

[0040] The cooling unit inlet pipe 11b is configured to have a size that allows it to be inserted into the outlet of the refrigerant passage of the chiller 16 and the refrigerant inlet of the connection device 100. Specifically, in this embodiment, the cooling unit inlet pipe 11b is a refrigerant pipe with an outer diameter of 15.88 mm from the inlet side to the outlet side. In contrast, the inner diameter of the outlet of the refrigerant passage of the chiller 16 and the inner diameter of a low flow inlet 131, which will be described later and through which the refrigerant flows into the connection device 100, are formed slightly larger than 15.88 mm. The outer diameter of the cooling unit inlet pipe 11b is the same as that of the air conditioning inlet pipe 11a.

[0041] The cooling unit inlet pipe 11b may be a refrigerant pipe having an outer diameter from the inlet side to the outlet side that is different from 15.88 mm. In this case, the refrigeration cycle apparatus 10 may be configured such that a refrigerant pipe conversion member having an outer diameter on the inlet side and an outer diameter on the outlet side that are different from each other is attached to the chiller 16 and the connection device 100, and the cooling unit inlet pipe 11b is connected to the chiller 16 and the connection device 100. The cooling unit inlet pipe 11b may be a refrigerant pipe having an outer diameter different from that of the air conditioning inlet pipe 11a.

[0042] The cooling section inlet piping 11b is provided with a third refrigerant temperature sensor 19c that detects the temperature of the refrigerant flowing out from the refrigerant passage of the chiller 16, and a third refrigerant pressure sensor 19f that detects the pressure of the refrigerant flowing out from the refrigerant passage of the chiller 16.

[0043] The third refrigerant temperature sensor 19c transmits a detection signal corresponding to the temperature of the refrigerant flowing out from the refrigerant passage of the chiller 16 to the control device 70. The third refrigerant pressure sensor 19f transmits a detection signal corresponding to the pressure of the refrigerant flowing out from the refrigerant passage of the chiller 16 to the control device 70.

[0044] The connection device 100 is a refrigerant pipe connection member that joins the refrigerant flowing in from the air conditioner inlet pipe 11a and the cooling unit inlet pipe 11b and guides it to the compressor outlet pipe 11c provided downstream of the refrigerant flow from the air conditioner inlet pipe 11a and the cooling unit inlet pipe 11b. The connection device 100 has a rapid flow inlet 121 that allows the refrigerant to flow into the connection device 100, a low flow inlet 131, and a refrigerant outlet 143 that allows the refrigerant that has flowed into the connection device 100 to flow out.

[0045] In the connection device 100, the air conditioning inlet pipe 11a is connected to the rapid flow inlet 121, the cooling section inlet pipe 11b is connected to the low flow inlet 131, and the compressor outlet pipe 11c is connected to the refrigerant outlet 143. The connection device 100 will be described in detail later.

[0046] The compressor outflow pipe 11c forms a refrigerant passage through which the refrigerant flows, and is connected at its upstream side in the refrigerant flow to the connection device 100 and at its downstream side in the refrigerant flow to the compressor 12. The compressor outflow pipe 11c is an outflow pipe that guides the refrigerant that flows out from the connection device 100 to the compressor 12.

[0047] The compressor outlet pipe 11c is configured to have a size that allows it to be inserted into the refrigerant suction port 12a of the compressor 12 and the refrigerant outlet port 143 of the connection device 100. Specifically, in this embodiment, the compressor outlet pipe 11c is a refrigerant pipe having an outer diameter of 19.05 mm from the inlet side to the outlet side. In contrast, the inner diameter of the refrigerant suction port 12a of the compressor 12 and the inner diameter of the refrigerant outlet port 143 of the connection device 100 are formed slightly larger than 19.05 mm. The outer diameter of the compressor outlet pipe 11c is larger than the outer diameters of the air conditioning inlet pipe 11a and the cooling section inlet pipe 11b.

[0048] The compressor outflow pipe 11c may be a refrigerant pipe having an outer diameter from the inlet side to the outlet side that is different from 19.05 mm. In this case, the refrigeration cycle device 10 may be configured such that a refrigerant pipe conversion member having an outer diameter on the inlet side and an outer diameter on the outlet side that are different from each other is attached to the connection device 100 and the compressor 12, and the compressor outflow pipe 11c is connected to the connection device 100 and the compressor 12. The compressor outflow pipe 11c may be a refrigerant pipe having the same outer diameter as the air conditioning inflow pipe 11a and the cooling unit inflow pipe 11b, or a refrigerant pipe having an outer diameter smaller than the air conditioning inflow pipe 11a and the cooling unit inflow pipe 11b.

[0049] Next, the high-temperature side heat medium circuit 30 will be described. The high-temperature side heat medium circuit 30 is a heat medium circulation circuit that circulates the high-temperature side heat medium. As the high-temperature side heat medium, a solution containing ethylene glycol, dimethylpolysiloxane, or nanofluid, antifreeze, etc. can be used. The high-temperature side heat medium circuit 30 includes a water passage of the water-refrigerant heat exchanger 13, a high-temperature side heat medium pump 31, an electric heater 32, a high-temperature side flow rate control valve 33, a high-temperature side radiator 34, a heater core 35, and a high-temperature side heat medium junction 36. Furthermore, the high-temperature side heat medium circuit 30 includes a first high-temperature side heat medium temperature sensor 37a and a second high-temperature side heat medium temperature sensor 37b that detect the temperature of the high-temperature side heat medium flowing through the high-temperature side heat medium circuit 30.

[0050] The high-temperature side heat medium pump 31 is a water pump that pumps the high-temperature side heat medium to the inlet side of the water passage of the water-refrigerant heat exchanger 13. The high-temperature side heat medium pump 31 is an electric pump whose rotation speed (i.e., pumping capacity) is controlled by a control voltage output from the control device 70.

[0051] An electric heater 32 is connected to the outlet of the water passage of the water-refrigerant heat exchanger 13. A first high-temperature side heat medium temperature sensor 37a is provided in the refrigerant passage on the outlet side of the water passage of the water-refrigerant heat exchanger 13 to detect the temperature of the high-temperature side heat medium flowing out from the outlet of the water passage of the water-refrigerant heat exchanger 13. The first high-temperature side heat medium temperature sensor 37a transmits a detection signal corresponding to the temperature of the high-temperature side heat medium flowing out from the outlet of the water passage of the water-refrigerant heat exchanger 13 to the control device 70.

[0052] The electric heater 32 is an auxiliary heating device that heats the high-temperature side heat medium flowing out from the water passage of the water-refrigerant heat exchanger 13. In the high-temperature side heat medium circuit 30, a PTC heater having a PTC element (i.e., a positive temperature coefficient thermistor) is adopted as the electric heater 32. The amount of heat generated by the electric heater 32 is controlled by a control voltage output from the control device 70. The refrigerant outlet of the electric heater 32 is connected to the inlet side of the high-temperature side flow rate adjustment valve 33, which has three inlet and outlets that can communicate with each other.

[0053] The high-temperature side flow rate control valve 33 has one inlet and two outlets, and is a high-temperature side flow rate ratio adjustment unit that adjusts the high-temperature side flow rate ratio, which is the flow rate of the high-temperature side heat medium flowing into heater core 35 relative to the flow rate of the high-temperature side heat medium flowing into high-temperature side radiator 34. The high-temperature side flow rate control valve 33 is an electric valve device that includes a valve body configured to be able to change its rotational position, and an electric actuator that changes the rotational position of the valve body.

[0054] The high-temperature side flow rate control valve 33 adjusts the high-temperature side flow ratio by adjusting the rotational position of the valve disc. In addition, the high-temperature side flow rate control valve 33 can also cause the high-temperature side heat medium that has flowed into the high-temperature side flow rate control valve 33 to flow out to only one of the high-temperature side radiator 34 and the heater core 35 by adjusting the rotational position of the valve disc.

[0055] The high-temperature side flow rate control valve 33 can change the usage mode of the high-temperature side heat medium by adjusting the high-temperature side flow rate ratio. The high-temperature side heat medium circuit 30 can heat the vehicle cabin by, for example, increasing the flow rate of the high-temperature side heat medium flowing into the heater core 35 with the high-temperature side flow rate control valve 33, using the heat of the high-temperature side heat medium to heat the blown air. On the other hand, the high-temperature side heat medium circuit 30 can release the heat of the high-temperature side heat medium to the outside air by, for example, increasing the flow rate of the high-temperature side heat medium flowing into the high-temperature side radiator 34 with the high-temperature side flow rate control valve 33. The operation of the high-temperature side flow rate control valve 33 is controlled by a control signal output from the control device 70.

[0056] The heat medium inlet side of the high-temperature side radiator 34 is connected to one of the outlets of the high-temperature side flow rate control valve 33. The heat medium inlet side of the heater core 35 is connected to the other outlet of the high-temperature side flow rate control valve 33. A second high-temperature side heat medium temperature sensor 37b that detects the temperature of the high-temperature side heat medium before it flows into the heater core 35 is provided in the refrigerant passage on the other outlet side of the high-temperature side flow rate control valve 33. The second high-temperature side heat medium temperature sensor 37b transmits a detection signal to the control device 70 according to the temperature of the high-temperature side heat medium before it flows out of the high-temperature side flow rate control valve 33 and flows into the heater core 35.

[0057] The high-temperature side radiator 34 is a high-temperature side outside air heat exchanger that exchanges heat between the high-temperature side heat medium heated in the water-refrigerant heat exchanger 13 and outside air blown by an outside air fan (not shown). The high-temperature side radiator 34 is disposed at the front side of the drive unit chamber. One inlet side of the high-temperature side heat medium junction 36 is connected to the heat medium outlet of the high-temperature side radiator 34.

[0058] The heater core 35 is a heating heat exchanger that heats the blown air by exchanging heat between the high-temperature side heat medium heated in the water-refrigerant heat exchanger 13 and the blown air that has passed through the indoor evaporator 14. The heater core 35 is disposed in an air conditioning case 51 of the indoor air conditioning unit 50. The other inlet side of the high-temperature side heat medium junction 36 is connected to the heat medium outlet of the heater core 35.

[0059] The high-temperature side heat medium junction 36 is a three-way joint that has two inlets and one outlet, and merges the refrigerant flowing in from the two inlets and flows out from one outlet. The outlet of the high-temperature side heat medium junction 36 is connected to the suction port side of the high-temperature side heat medium pump 31. The high-temperature side heat medium junction 36 guides the high-temperature side heat medium that flows in from the high-temperature side radiator 34 and the heater core 35 to the high-temperature side heat medium pump 31.

[0060] In the high-temperature side heat medium circuit 30 configured in this manner, the high-temperature side heat medium pump 31 and the high-temperature side flow rate adjustment valve 33 adjust the flow rate of the high-temperature side heat medium flowing into the heater core 35, thereby adjusting the amount of heat released from the high-temperature side heat medium in the heater core 35 to the blown air. In other words, the high-temperature side heat medium circuit 30 can adjust the amount of heat of the blown air in the heater core 35.

[0061] In other words, in this embodiment, the water-refrigerant heat exchanger 13 and the various components of the high-temperature side heat medium circuit 30 form a heating section that heats the blown air using the refrigerant discharged from the compressor 12 as a heat source.

[0062] Next, the low-temperature side heat medium circuit 40 will be described. The low-temperature side heat medium circuit 40 is a heat medium circulation circuit that circulates the low-temperature side heat medium. As the low-temperature side heat medium, the same fluid as the high-temperature side heat medium can be used. The low-temperature side heat medium circuit 40 includes a water passage for the chiller 16, a low-temperature side heat medium pump 41, a battery side three-way valve 42, a low-temperature side radiator 43, a cooling water passage for the battery 60, and an electrical equipment passage 44. The low-temperature side heat medium circuit 40 also includes a first low-temperature side heat medium junction 45a and a second low-temperature side heat medium junction 45b that join the low-temperature side heat medium flowing from a plurality of refrigerant passages, and a low-temperature side heat medium branching section 46 that branches the refrigerant flow into a plurality of refrigerant passages. The low-temperature side heat medium circuit 40 also includes a first low-temperature side heat medium temperature sensor 47a to a third low-temperature side heat medium temperature sensor 47c that detect the temperature of the low-temperature side heat medium flowing through the low-temperature side heat medium circuit 40.

[0063] The low-temperature side heat medium pump 41 is a water pump that pressure-feeds the low-temperature side heat medium to the inlet side of the water passage of the chiller 16. The basic configuration of the low-temperature side heat medium pump 41 is similar to that of the high-temperature side heat medium pump 31. The inlet side of the water passage of the chiller 16 is connected to the heat medium discharge side of the low-temperature side heat medium pump 41. The inlet side of the cell-side three-way valve 42 is connected to the outlet of the water passage of the chiller 16.

[0064] The battery-side three-way valve 42 has one inlet and two outlets, and is a low-temperature side flow rate ratio adjuster that adjusts the low-temperature side flow rate ratio of the low-temperature side heat medium flowing into the coolant passage of the battery 60 relative to the flow rate of the low-temperature side heat medium flowing into the low-temperature side radiator 43. One outlet of the battery-side three-way valve 42 is connected to the heat medium inlet side of the low-temperature side radiator 43 via a first low-temperature side heat medium junction 45a, and the other outlet is connected to the inlet side of the coolant passage of the battery 60. The battery-side three-way valve 42 and an equipment-side three-way valve 44c described later are basically configured similarly to the high-temperature side flow rate adjustment valve 33.

[0065] The battery-side three-way valve 42 adjusts the low-temperature side flow ratio by adjusting the rotational position of the valve body. The battery-side three-way valve 42 can also allow the low-temperature side heat medium that has flowed into it to flow out only to either the low-temperature side radiator 43 or the coolant passage of the battery 60.

[0066] For example, the battery-side three-way valve 42 fully closes one outlet and opens the other outlet, thereby passing the entire flow rate of the low-temperature side heat medium flowing out from the outlet of the water passage of the chiller 16 through the cooling water passage of the battery 60 and returning it to the suction side of the equipment pump 44b. On the other hand, the battery-side three-way valve 42 opens one outlet and fully closes the other outlet, thereby passing the entire flow rate of the low-temperature side heat medium flowing out from the outlet of the water passage of the chiller 16 through the low-temperature side radiator 43 and returning it to the suction side of the equipment pump 44b. The operation of the battery-side three-way valve 42 is controlled by a control signal output from the control device 70.

[0067] A first low-temperature side heat medium temperature sensor 47a is provided in the refrigerant passage on the other outlet side of the battery-side three-way valve 42 to detect the temperature of the low-temperature side heat medium before it flows into the cooling water passage of the battery 60. The first low-temperature side heat medium temperature sensor 47a transmits a detection signal to the control device 70 in accordance with the temperature of the low-temperature side heat medium before it flows out from the outlet of the water passage of the chiller 16 and into the cooling water passage of the battery 60.

[0068] The first low-temperature side heat medium junction 45a is a three-way joint having a basic configuration similar to that of the high-temperature side heat medium junction 36. The first low-temperature side heat medium junction 45a has one inlet connected to one outlet side of the battery-side three-way valve 42, the other inlet connected to the refrigerant flow downstream side of the electric equipment passage 44, and the outlet connected to the heat medium inlet side of the low-temperature side radiator 43. The first low-temperature side heat medium junction 45a guides the refrigerant flowing in from the battery-side three-way valve 42 and the electric equipment passage 44 to the low-temperature side radiator 43.

[0069] The low-temperature side radiator 43 is a low-temperature side outside air heat exchanger that exchanges heat between the low-temperature side heat medium flowing out from the battery-side three-way valve 42 and outside air blown by an outside air fan (not shown). The low-temperature side radiator 43 is disposed on the front side of the drive unit chamber, downstream of the high-temperature side radiator 34 in the flow of outside air.

[0070] Therefore, low-temperature side radiator 43 exchanges heat between the low-temperature side heat medium and the outside air that has passed through high-temperature side radiator 34. Low-temperature side radiator 43 may be formed integrally with high-temperature side radiator 34. One inlet side of second low-temperature side heat medium junction 45b is connected to a heat medium outlet of low-temperature side radiator 43 via low-temperature side heat medium branching section 46.

[0071] Further, a second low-temperature side heat medium temperature sensor 47b is provided in the refrigerant passage on the heat medium outlet side of low-temperature side radiator 43 to detect the temperature of the low-temperature side heat medium flowing out from low-temperature side radiator 43. The second low-temperature side heat medium temperature sensor 47b transmits a detection signal corresponding to the temperature of the low-temperature side heat medium flowing out from low-temperature side radiator 43 to the control device 70. The second low-temperature side heat medium temperature sensor 47b is provided to determine the presence or absence of frost on the low-temperature side radiator 43 based on the temperature of the low-temperature side heat medium flowing out from low-temperature side radiator 43.

[0072] The low-temperature side heat medium branching section 46 is a three-way joint having one inlet and two outlets, which branches the refrigerant flowing in from the inlet and flows out from one outlet and the other outlet. One outlet of the low-temperature side heat medium branching section 46 is connected to one inlet side of the second low-temperature side heat medium junction 45b, and the other outlet is connected to the upstream side of the refrigerant flow of the electrical equipment passage 44. The low-temperature side heat medium branching section 46 guides the refrigerant flowing in from the low-temperature side radiator 43 to the second low-temperature side heat medium junction 45b and the electrical equipment passage 44.

[0073] The second low-temperature side heat medium junction 45b has one inlet connected to one outlet side of the low-temperature side heat medium branch section 46, the other inlet connected to the outlet side of the coolant passage of the battery 60, and the outlet connected to the suction port side of the low-temperature side heat medium pump 41. The second low-temperature side heat medium junction 45b guides the refrigerant flowing in from the low-temperature side radiator 43 and the coolant passage of the battery 60 to the low-temperature side heat medium pump 41.

[0074] The battery 60 stores power to be supplied to multiple electrical devices. The battery 60 is an assembled battery formed by electrically connecting multiple battery cells (not shown) in series or parallel. The battery cells are chargeable and dischargeable secondary batteries (lithium ion batteries in this embodiment). The battery 60 is configured by stacking multiple battery cells to form a substantially rectangular parallelepiped shape and housing them in a dedicated case.

[0075] This type of secondary battery generates heat during operation (i.e., during charging and discharging). Secondary batteries are prone to deterioration when exposed to high temperatures. Furthermore, chemical reactions in secondary batteries do not proceed easily when exposed to low temperatures, and output is prone to decrease. For this reason, it is desirable to maintain the temperature of the secondary battery within an appropriate temperature range (e.g., 15°C or higher and 55°C or lower) that allows the secondary battery's charge and discharge capacity to be fully utilized.

[0076] Therefore, in this embodiment, a cooling water passage for circulating the low-temperature side heat medium is formed inside the dedicated case of the battery 60. The cooling water passage has a passage configuration in which a plurality of passages are connected in parallel inside the dedicated case. As a result, the cooling water passage is formed so that the temperature of all the battery cells can be adjusted evenly. Therefore, the battery 60 in this embodiment is the object to be cooled. The outlet of the cooling water passage of the battery 60 is connected to the other inlet side of the second low-temperature side heat medium junction 45b.

[0077] Therefore, in the low-temperature side heat medium circuit 40, the low-temperature side heat medium pump 41 and the battery-side three-way valve 42 adjust the flow rate of the low-temperature side heat medium flowing into the coolant passage of the battery 60, thereby adjusting the amount of heat absorbed by the low-temperature side heat medium from the battery 60. That is, in this embodiment, the chiller 16 and the components of the low-temperature side heat medium circuit 40 form a cooling section that evaporates the refrigerant flowing out from the second expansion valve 17b to cool the battery 60.

[0078] Furthermore, an electric equipment passage 44 is connected to the low-temperature side heat medium circuit 40 of this embodiment. The electric equipment passage 44 is a heat medium passage that returns the refrigerant flowing out from the heat medium outlet side of the low-temperature side radiator 43 to the heat medium inlet side of the low-temperature side radiator 43, and is connected to the low-temperature side heat medium branching section 46 on one side and to the first low-temperature side heat medium junction 45a on the other side. In the electric equipment passage 44, an equipment passage junction 44a, an equipment pump 44b, a cooling water passage for the inverter 61, a cooling water passage for the motor generator 62, a cooling water passage for the transaxle device 63, an equipment side three-way valve 44c, etc. are arranged.

[0079] The equipment passage junction 44a is a three-way joint having a basic configuration similar to that of the first low-temperature side heat medium junction 45a and the second low-temperature side heat medium junction 45b. The equipment passage junction 44a has one inlet connected to the other outlet of the low-temperature side heat medium branch 46, and the other inlet connected to the downstream side of the refrigerant flow of the bypass passage 44d that bypasses the low-temperature side radiator 43. The outlet of the equipment passage junction 44a is connected to the suction port side of the equipment pump 44b. The equipment passage junction 44a guides the refrigerant flowing in from the low-temperature side heat medium branch 46 and the bypass passage 44d to the equipment pump 44b.

[0080] The equipment pump 44b is a water pump that pumps at least a part of the low-temperature side heat medium flowing out from the low-temperature side radiator 43 to a cooling water passage of the inverter 61. The equipment pump 44b has the same basic configuration as the low-temperature side heat medium pump 41.

[0081] The inverter 61 is one of a plurality of electric devices directly connected to the battery 60. The inverter 61 is a power conversion device that converts DC power output from the battery 60 into AC power and supplies it to the motor generator 62. Furthermore, the inverter 61 can also convert AC power generated by the motor generator 62 into DC power and output it to the battery 60. The operation of the inverter 61 is controlled by a control signal output from the control device 70.

[0082] The inverter 61 generates heat during operation. When the inverter 61 becomes hot, the electrical circuit of the inverter 61 is likely to deteriorate. For this reason, the temperature of the inverter 61 needs to be maintained at a temperature lower than the standard heat resistance temperature (for example, 130° C. or lower) at which the electrical circuit can be protected.

[0083] Therefore, in this embodiment, a cooling water passage for circulating the low-temperature side heat medium is formed in a housing portion forming an outer shell of the inverter 61. The cooling water passage of the inverter 61 is a heat exchange portion for exchanging heat between the low-temperature side heat medium and the inverter 61. The outlet of the cooling water passage of the inverter 61 is connected to the inlet side of the cooling water passage of the motor generator 62.

[0084] The motor generator 62 is one of a plurality of electric devices indirectly connected to the battery 60. The motor generator 62 is an electric motor for traveling that outputs driving force for traveling using electric power supplied from the inverter 61. Furthermore, the motor generator 62 is a power generation device that generates regenerative electric power when the vehicle is decelerating or traveling downhill.

[0085] The motor generator 62 generates heat during operation. When the motor generator 62 becomes hot, the deterioration of the electric circuitry tends to progress. Furthermore, when the motor generator 62 becomes cold, the sliding resistance increases, making it difficult to output a smooth rotational drive force. For this reason, the temperature of the motor generator 62 needs to be maintained within an appropriate temperature range (e.g., 80°C or higher and 130°C or lower) that can protect the electric circuitry and output a smooth rotational drive force.

[0086] Therefore, in this embodiment, a cooling water passage for circulating the low-temperature side heat medium is formed in a housing portion that forms the outer shell of the motor generator 62. The cooling water passage of the motor generator 62 is a heat exchange portion that exchanges heat between the low-temperature side heat medium and the motor generator 62. The outlet of the cooling water passage of the motor generator 62 is connected to the inlet side of the cooling water passage of the transaxle device 63.

[0087] The transaxle device 63 is one of a plurality of electric devices indirectly connected to the battery 60. The transaxle device 63 is a device that integrates a transmission, a final gear, and a differential gear.

[0088] The transaxle unit 63 generates heat during operation. When the temperature of the transaxle unit 63 becomes high, deterioration of the electrical circuits of the transaxle unit 63 progresses. Furthermore, when the temperature of the transaxle unit 63 becomes low, it becomes difficult for the oil that lubricates the transaxle unit 63 to circulate. For this reason, the temperature of the transaxle unit 63 must be maintained within an appropriate temperature range (e.g., −10° C. or higher and 60° C. or lower) that can protect the electrical circuits and ensure smooth oil circulation.

[0089] Therefore, in this embodiment, a cooling water passage for circulating the low-temperature side heat medium is formed in a housing portion forming the outer shell of the transaxle unit 63. The cooling water passage of the transaxle unit 63 is a heat exchange portion for exchanging heat between the low-temperature side heat medium and the transaxle unit 63. The outlet of the cooling water passage of the transaxle unit 63 is connected to the inlet side of the equipment-side three-way valve 44c.

[0090] Further, a third low-temperature side heat medium temperature sensor 47c is provided in the refrigerant passage on the outlet side of the coolant passage of the transaxle unit 63 to detect the temperature of the low-temperature side heat medium flowing out from the transaxle unit 63. The third low-temperature side heat medium temperature sensor 47c transmits a detection signal corresponding to the temperature of the low-temperature side heat medium flowing out from the transaxle unit 63 to the control device 70.

[0091] The equipment-side three-way valve 44c has one inlet and two outlets, and is a low-temperature side flow rate ratio adjuster that adjusts the low-temperature side flow rate ratio of the low-temperature side heat medium flowing into the bypass passage 44d relative to the low-temperature side heat medium flowing into the low-temperature side radiator 43. One outlet of the equipment-side three-way valve 44c is connected to the other inlet of the first low-temperature side heat medium junction 45a, and the other outlet is connected to the upstream side of the refrigerant flow of the bypass passage 44d.

[0092] The equipment-side three-way valve 44c adjusts the flow rate ratio between the flow rate of the low-temperature side heat medium flowing into the low-temperature side radiator 43 and the flow rate of the low-temperature side heat medium flowing into the bypass passage 44d by adjusting the rotational position of the valve body. The equipment-side three-way valve 44c can also cause the low-temperature side heat medium that has flowed inside to flow out to only one of the low-temperature side radiator 43 and the bypass passage 44d.

[0093] The equipment-side three-way valve 44c fully closes one outlet and opens the other outlet, thereby causing the entire flow rate of the low-temperature side heat medium flowing out of the cooling water passage of the transaxle device 63 to bypass the low-temperature side radiator 43 and return it to the suction side of the equipment pump 44b. On the other hand, the equipment-side three-way valve 44c opens one outlet and fully closes the other outlet, thereby causing the entire flow rate of the low-temperature side heat medium flowing out of the cooling water passage of the transaxle device 63 to pass through the low-temperature side radiator 43 and return it to the suction side of the equipment pump 44b. The operation of the equipment-side three-way valve 44c is controlled by a control signal output from the control device 70.

[0094] In this way, the battery-side three-way valve 42 and the device-side three-way valve 44 c also function as a low-temperature side heat medium circuit switching unit that switches the circuit configuration of the low-temperature side heat medium circuit 40 .

[0095] Next, the interior air conditioning unit 50 will be described. The interior air conditioning unit 50 is for blowing out the ventilation air whose temperature has been adjusted by the refrigeration cycle device 10 into the vehicle interior. The interior air conditioning unit 50 is disposed inside the instrument panel (i.e., the instrument panel) at the frontmost part of the vehicle interior.

[0096] As shown in FIG. 1, the indoor air conditioning unit 50 houses an indoor / outdoor air switching device 52, a blower 53, an indoor evaporator 14, a heater core 35, an evaporator temperature sensor 54, an air mix door 56, etc. in an air passage formed in an air conditioning case 51 that forms the outer shell of the indoor air conditioning unit 50.

[0097] The air conditioning case 51 forms an air passage for blowing air into the vehicle interior. The air conditioning case 51 is molded from a resin (such as polypropylene) that has a certain degree of elasticity and excellent strength.

[0098] An inside / outside air switching device 52 is disposed on the most upstream side of the blown air flow of the air conditioning case 51. The inside / outside air switching device 52 switches the air introduced into the air conditioning case 51 between inside air (i.e., air inside the vehicle cabin) and outside air (i.e., air outside the vehicle cabin).

[0099] The inside / outside air switching device 52 continuously adjusts the opening area of ​​the inside air inlet 52a for introducing inside air into the air conditioning case 51 and the outside air inlet 52b for introducing outside air into the air conditioning case 51 by the inside / outside air switching door 52c, thereby changing the ratio of the amount of inside air introduced to the amount of outside air introduced. The inside / outside air switching door 52c is driven by an electric actuator (not shown) for the inside / outside air switching door 52c. The operation of this electric actuator is controlled by a control signal output from the control device 70. A blower 53 is disposed downstream of the inside / outside air switching device 52 in the flow of blown air.

[0100] The blower 53 blows the air drawn in through the inside / outside air switching device 52 toward the vehicle interior. The blower 53 is an electric blower in which a centrifugal multi-blade fan 53a is driven by an electric motor 53b. The rotation speed (i.e., blowing capacity) of the blower 53 is controlled by a control voltage output from the control device 70.

[0101] The indoor evaporator 14 and the heater core 35 are disposed in this order with respect to the flow of the blown air downstream of the blower 53. That is, the indoor evaporator 14 is disposed upstream of the heater core 35 with respect to the flow of the blown air.

[0102] The interior evaporator 14 is provided with an evaporator temperature sensor 54 that detects the refrigerant evaporation temperature (i.e., the evaporator temperature) in the interior evaporator 14. Specifically, the evaporator temperature sensor 54 detects the heat exchange fin temperature of the interior evaporator 14. The evaporator temperature sensor 54 transmits a detection signal corresponding to the refrigerant evaporation temperature of the interior evaporator 14 to the control device 70.

[0103] A cold air bypass passage 55 is provided in the air conditioning case 51, which allows the blown air after passing through the indoor evaporator 14 to flow around the heater core 35. An air mix door 56 is disposed downstream of the indoor evaporator 14 in the air conditioning case 51 and upstream of the heater core 35 in the blown air flow.

[0104] The air mix door 56 is an air volume ratio adjustment unit that adjusts the ratio of the volume of the blown air passing through the heater core 35 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 14. The air mix door 56 is driven by an electric actuator (not shown) for the air mix door 56. The operation of this electric actuator is controlled by a control signal output from the control device 70.

[0105] A mixing space 57 is disposed downstream of the blown air flow of the cold air bypass passage 55 inside the air conditioning case 51. The mixing space 57 is a space where the blown air heated by the heater core 35 and the blown air that has passed through the cold air bypass passage 55 and has not been heated are mixed.

[0106] Furthermore, an opening hole is arranged downstream of the blown air flow of the air conditioning case 51 for blowing the blown air mixed in the mixing space 57 (that is, the conditioned air) into the vehicle cabin, which is the space to be air conditioned.

[0107] The openings include a face opening, a foot opening, and a defroster opening, all of which are not shown in the figure. The face opening is an opening for blowing conditioned air toward the upper bodies of passengers in the vehicle cabin. The foot opening is an opening for blowing conditioned air toward the feet of passengers. The defroster opening is an opening for blowing conditioned air toward the inside surface of the vehicle front windshield.

[0108] These face opening hole, foot opening hole, and defroster opening hole are connected to a face air outlet, a foot air outlet, and a defroster air outlet, none of which are shown, provided in the vehicle cabin, via ducts that form air passages, respectively.

[0109] Therefore, the air mix door 56 adjusts the ratio of the amount of air passing through the heater core 35 and the amount of air passing through the cold air bypass passage 55, thereby adjusting the temperature of the conditioned air mixed in the mixing space 57. And the temperature of the blown air (i.e., the conditioned air) blown into the vehicle compartment from each air outlet is adjusted.

[0110] A face door, a foot door, and a defroster door (all not shown) are disposed upstream of the face opening hole, the foot opening hole, and the defroster opening hole in the flow of blown air, respectively. The face door adjusts the opening area of ​​the face opening hole. The foot door adjusts the opening area of ​​the foot opening hole. The defroster door adjusts the opening area of ​​the frost opening hole.

[0111] The face door, foot door, and defroster door constitute an air outlet mode switching device that switches the air outlet mode. These doors are connected to an electric actuator for driving the air outlet mode door via a link mechanism or the like, and are rotated in conjunction with each other. The operation of this electric actuator is also controlled by a control signal output from the control device 70.

[0112] Specific examples of the air outlet modes that can be switched by the air outlet mode switching device include a face mode, a bi-level mode, and a foot mode.

[0113] The face mode is an outlet mode in which the face outlet is fully opened and air is blown from the face outlet toward the upper body of the vehicle occupant. The bi-level mode is an outlet mode in which both the face outlet and the foot outlet are opened and air is blown toward the upper body and feet of the vehicle occupant. The foot mode is an outlet mode in which the foot outlet is fully opened and the defroster outlet is only slightly opened and air is mainly blown from the foot outlet.

[0114] Furthermore, the mode can be switched to the defroster mode by the passenger manually operating a blowing mode changeover switch provided on the operation panel 71 described later. The defroster mode is a blowing port mode in which the defroster blowing port is fully opened and air is blown out from the defroster blowing port onto the inner surface of the windshield.

[0115] Next, an overview of the control device 70 of this embodiment will be described with reference to Fig. 2. The control device 70 is composed of a microcomputer including a CPU, ROM, RAM, etc., and its peripheral circuits. The control device 70 performs various calculations and processes based on an air conditioning control program stored in the ROM, and controls the operation of various control target devices connected to the output side. The ROM and RAM of the control device 70 are composed of non-transient substantial storage media.

[0116] 2, the above-mentioned first refrigerant temperature sensor 19a to third refrigerant temperature sensor 19c and first refrigerant pressure sensor 19d to third refrigerant pressure sensor 19f are connected to the input side of the control device 70. The above-mentioned first high temperature side heat medium temperature sensor 37a, second high temperature side heat medium temperature sensor 37b, first low temperature side heat medium temperature sensor 47a to third low temperature side heat medium temperature sensor 47c, and evaporator temperature sensor 54 are connected to the input side of the control device 70. Furthermore, an inside air temperature sensor 72, an outside air temperature sensor 73, a solar radiation sensor 74, etc. are connected to the input side of the control device 70. Detection signals of these sensors are input to the control device 70.

[0117] The inside air temperature sensor 72 is an inside air temperature detector that detects the temperature inside the vehicle cabin (inside air temperature). The outside air temperature sensor 73 is an outside air temperature detector that detects the temperature outside the vehicle cabin (outside air temperature). The solar radiation sensor 74 is an insolation amount detector that detects the amount of solar radiation irradiated into the vehicle cabin.

[0118] Furthermore, an operation panel 71 arranged near the instrument panel at the front of the vehicle interior is connected to the input side of the control device 70, and operation signals are input from various operation switches provided on this operation panel 71.

[0119] Specific examples of the various operation switches provided on the operation panel 71 include an auto switch for setting or canceling the automatic control operation of the vehicle air conditioner 1, and an air conditioner switch for requesting cooling of the blown air by the interior evaporator 14 or heating of the blown air by the heater core 35. Other examples of the various operation switches include an air volume setting switch for manually setting the air volume of the blower 53, a temperature setting switch for setting a target temperature in the vehicle cabin, and a blowing mode changeover switch for manually setting the blowing mode.

[0120] 2, the output side of the control device 70 is connected to the compressor 12, the high-temperature side heat medium pump 31, the low-temperature side heat medium pump 41, the equipment pump 44b, the blower 53, the air mix door 56, and the electric heater 32. The output side of the control device 70 is connected to electric actuators that operate the first expansion valve 17a, the second expansion valve 17b, the high-temperature side flow control valve 33, the battery side three-way valve 42, and the equipment side three-way valve 44c. The output side of the control device 70 is connected to the inverter 61, the motor generator 62, the transaxle device 63, and the like. The control device 70 of this embodiment controls the operation of various control target devices and the like connected to its output side.

[0121] Next, the operation of the present embodiment in the above configuration will be described. As described above, the vehicle air conditioner 1 of the present embodiment has a function of not only heating and cooling the air to be blown into the vehicle compartment, but also cooling the battery 60. Therefore, the refrigeration cycle device 10 can switch the refrigerant circuit to operate in the following operation modes.

[0122] These driving modes are switched by executing an air conditioning control program. The air conditioning control program is executed by the control device 70 based on detection signals detected by the inside air temperature sensor 72, the outside air temperature sensor 73, the solar radiation sensor 74, etc. when the automatic control of the vehicle interior is set by turning on the auto switch of the operation panel 71 by the occupant's operation.

[0123] (1) Cooling mode The cooling mode is an operation mode in which the interior of the vehicle is cooled without cooling the battery 60.

[0124] In the cooling mode, the control device 70 switches the refrigeration cycle device 10 to a refrigerant circuit for the cooling mode. Specifically, the control device 70 throttles the first expansion valve 17a and fully closes the second expansion valve 17b. Based on detection signals transmitted from the second refrigerant temperature sensor 19b and the second refrigerant pressure sensor 19e, the control device 70 determines the opening degree of the first expansion valve 17a so that the degree of superheat of the refrigerant on the outlet side of the indoor evaporator 14 becomes a predetermined target degree of superheat.

[0125] The control device 70 also adjusts the rotational position of the valve disc of the high-temperature side flow rate control valve 33 so that the high-temperature side heat medium flowing into the high-temperature side flow rate control valve 33 does not flow into the heater core 35, but flows only into the high-temperature side radiator 34. Furthermore, the control device 70 adjusts the rotational position of the valve disc of the equipment-side three-way valve 44c so that the low-temperature side heat medium flowing into the equipment-side three-way valve 44c does not flow into the bypass passage 44d, but flows only into the low-temperature side radiator 43. The control device 70 also brings the battery-side three-way valve 42 into a fully closed state.

[0126] Furthermore, the control device 70 operates the electric actuator of the air mix door 56 so that the entire amount of the blown air that has passed through the indoor evaporator 14 passes through the cold air bypass passage 55. Then, the control device 70 outputs control signals to operate the compressor 12, the high temperature side heat medium pump 31, the equipment pump 44b, and the blower 53.

[0127] Therefore, in the refrigeration cycle apparatus 10 in the cooling mode, the refrigerant circulates in the order of the compressor 12 → water-refrigerant heat exchanger 13 → refrigerant branching section 18 → first expansion valve 17a → indoor evaporator 14 → air conditioning inlet pipe 11a → connection device 100 → compressor outlet pipe 11c → compressor 12. In the refrigeration cycle apparatus 10 in the cooling mode, the second expansion valve 17b is fully closed, so that the refrigerant does not flow into the cooling section inlet pipe 11b.

[0128] In the high-temperature side heat medium circuit 30 in the cooling mode, the high-temperature side heat medium pump 31 causes the high-temperature side heat medium flowing out of the water passage of the water-refrigerant heat exchanger 13 to flow to the high-temperature side radiator 34 and return to the suction side of the high-temperature side heat medium pump 31.

[0129] In the low-temperature side heat medium circuit 40 in the cooling mode, the low-temperature side heat medium circulates in the following order: equipment pump 44b → cooling water passage of the inverter 61 → cooling water passage of the motor generator 62 → cooling water passage of the transaxle device 63 → low-temperature side radiator 43 → equipment pump 44b.

[0130] Thus, in the cooling mode, the refrigerant flowing out from the indoor evaporator 14 flows into the connection device 100 from the rapid inlet 121 via the air conditioning inlet piping 11a, but the refrigerant does not flow in from the low inlet 131. Then, the connection device 100 causes the refrigerant that flows in from the rapid inlet 121 to flow out from the refrigerant outlet 143 and guides it to the compressor outlet piping 11c.

[0131] In the refrigeration cycle apparatus 10 in the cooling mode, the water-refrigerant heat exchanger 13 heats the high-temperature side heat medium using the refrigerant discharged from the compressor 12 as a heat source, and the first expansion valve 17a reduces the pressure of the refrigerant flowing out from the water-refrigerant heat exchanger 13. In the refrigeration cycle apparatus 10, the indoor evaporator 14 absorbs heat from the blown air blown by the blower 53 to evaporate the refrigerant and cool the blown air.

[0132] In the high-temperature side heat medium circuit 30 in the cooling mode, the high-temperature side radiator 34 radiates heat from the high-temperature side heat medium heated in the water-refrigerant heat exchanger 13. In the low-temperature side heat medium circuit 40 in the cooling mode, the low-temperature side radiator 43 radiates heat from the low-temperature side heat medium heated by the heat generated by the inverter 61, the motor generator 62, and the transaxle device 63.

[0133] Therefore, in the vehicle air conditioner 1 in the cooling mode, the vehicle interior can be cooled by blowing out the blown air cooled by the interior evaporator 14 into the vehicle interior. Also, in the vehicle air conditioner 1 in the cooling mode, the low-temperature side heat medium cooled by the low-temperature side radiator 43 is circulated in the low-temperature side heat medium circuit 40, thereby cooling the inverter 61, the motor generator 62, and the transaxle device 63.

[0134] (2) Heating mode The heating mode is an operation mode in which the battery 60 is not cooled but the interior of the vehicle is heated.

[0135] In the heating mode, the control device 70 switches the refrigeration cycle device 10 to a refrigerant circuit for the heating mode. Specifically, the control device 70 fully closes the first expansion valve 17a and throttles the second expansion valve 17b. Based on detection signals transmitted from the third refrigerant temperature sensor 19c and the third refrigerant pressure sensor 19f, the control device 70 determines the opening degree of the second expansion valve 17b so that the degree of subcooling of the refrigerant on the outlet side of the chiller 16 becomes a predetermined target degree of subcooling.

[0136] In addition, the control device 70 adjusts the rotational position of the valve body of the high-temperature side flow rate control valve 33 so that the high-temperature side heat medium flowing into the high-temperature side flow rate control valve 33 does not flow into the high-temperature side radiator 34, but flows only into the heater core 35.

[0137] Furthermore, the control device 70 adjusts the rotational position of the valve disc of the battery-side three-way valve 42 so that the low-temperature side heat medium flowing into the battery-side three-way valve 42 does not flow into the cooling water passage of the battery 60, but flows only into the low-temperature side radiator 43. The control device 70 then adjusts the rotational position of the valve disc of the equipment-side three-way valve 44c so that the low-temperature side heat medium flowing into the equipment-side three-way valve 44c does not flow into the low-temperature side radiator 43, but flows only into the bypass passage 44d.

[0138] The control device 70 also operates the electric actuator of the air mix door 56 so that the entire volume of the blown air that has passed through the indoor evaporator 14 passes through the heater core 35. Furthermore, the control device 70 adjusts the heating capacity of the electric heater 32 as necessary based on a detection signal transmitted from the first high-temperature side heat medium temperature sensor 37a so that the temperature of the high-temperature side heat medium flowing out of the heater core 35 becomes equal to or higher than a predetermined reference temperature.

[0139] Based on the detection signal transmitted from the second high-temperature side heat medium temperature sensor 37b, the control device 70 adjusts the rotation speed of the compressor 12. The control device 70 also outputs control signals for operating the high-temperature side heat medium pump 31, the low-temperature side heat medium pump 41, and the blower 53.

[0140] Therefore, in the refrigeration cycle apparatus 10 in the heating mode, the refrigerant circulates in the following order: compressor 12 → water-refrigerant heat exchanger 13 → refrigerant branching section 18 → second expansion valve 17b → chiller 16 → cooling section inlet pipe 11b → connection device 100 → compressor outlet pipe 11c → compressor 12. In the refrigeration cycle apparatus 10 in the heating mode, the first expansion valve 17a is fully closed, so that the refrigerant does not flow into the air conditioning inlet pipe 11a.

[0141] In the high-temperature side heat medium circuit 30 in the heating mode, the high-temperature side heat medium pump 31 causes the high-temperature side heat medium flowing out of the water passage of the water-refrigerant heat exchanger 13 to flow to the heater core 35 and return to the suction port of the high-temperature side heat medium pump 31.

[0142] In the low-temperature side heat medium circuit 40 in the heating mode, the low-temperature side heat medium pump 41 causes the low-temperature side heat medium flowing out of the water passage of the chiller 16 to flow to the low-temperature side radiator 43 and return to the suction port of the low-temperature side heat medium pump 41. Furthermore, in the low-temperature side heat medium circuit 40 in the heating mode, the low-temperature side heat medium circulates in the following order: equipment pump 44b → cooling water passage of the inverter 61 → cooling water passage of the motor generator 62 → cooling water passage of the transaxle unit 63 → bypass passage 44d → equipment pump 44b.

[0143] Thus, in the heating mode, the refrigerant flowing out from the chiller 16 flows into the connection device 100 from the low inlet 131 via the cooling section inlet piping 11b, but the refrigerant does not flow into the connection device 100 from the rapid inlet 121. Then, the connection device 100 causes the refrigerant that flows in from the low inlet 131 to flow out from the refrigerant outlet 143 and guides it to the compressor outlet piping 11c.

[0144] In the refrigeration cycle apparatus 10 in the heating mode, the water-refrigerant heat exchanger 13 heats the high-temperature side heat medium using the refrigerant discharged from the compressor 12 as a heat source, and the second expansion valve 17b reduces the pressure of the refrigerant flowing out from the water-refrigerant heat exchanger 13. In the refrigeration cycle apparatus 10, the chiller 16 absorbs heat from the low-temperature side heat medium flowing through the low-temperature side heat medium circuit 40 to cool the low-temperature side heat medium.

[0145] In addition, in the high-temperature side heat medium circuit 30 in the heating mode, the high-temperature side heat medium heated by the water-refrigerant heat exchanger 13 and the electric heater 32 exchanges heat with the blown air blown from the blower 53 in the heater core 35, heating the blown air.

[0146] In the low-temperature side heat medium circuit 40 in the heating mode, the low-temperature side radiator 43 heats the low-temperature side heat medium by absorbing heat from the outside air that has passed through the high-temperature side radiator 34. The heated low-temperature side heat medium then exchanges heat with the refrigerant circulating through the refrigeration cycle device 10 in the chiller 16 to heat the refrigerant. Furthermore, in the low-temperature side heat medium circuit 40 in the heating mode, the low-temperature side heat medium heated by the self-heating of the inverter 61, the motor generator 62, and the transaxle device 63 can be circulated via the bypass passage 44d.

[0147] Therefore, in the vehicle air conditioner 1 in the heating mode, the interior of the vehicle can be heated by blowing out the blown air heated by the heater core 35 into the vehicle interior. Furthermore, the refrigerant circulating in the refrigeration cycle device 10 can be heated by exchanging heat between the heated low-temperature side heat medium and the refrigerant to heat the refrigerant.

[0148] Furthermore, the heat generated by the operation of the inverter 61 , the motor generator 62 , and the transaxle device 63 can be used to heat the inverter 61 , the motor generator 62 , and the transaxle device 63 .

[0149] (3) Dehumidifying heating mode The dehumidifying and heating mode is an operation mode in which the interior of the vehicle is dehumidified and heated without cooling the battery 60.

[0150] In the dehumidifying and heating mode, the control device 70 switches the refrigeration cycle device 10 to a refrigerant circuit for the dehumidifying and heating mode. Specifically, the control device 70 throttles the first expansion valve 17a. Based on detection signals transmitted from the second refrigerant temperature sensor 19b and the second refrigerant pressure sensor 19e, the control device 70 determines the opening degree of the first expansion valve 17a so that the degree of superheat of the refrigerant on the outlet side of the indoor evaporator 14 becomes a predetermined target degree of superheat.

[0151] Furthermore, the control device 70 throttles or fully closes the second expansion valve 17b in accordance with the target temperature in the vehicle cabin set by the temperature setting switch, etc. When the control device 70 throttles the second expansion valve 17b, it determines the opening degree based on detection signals transmitted from the third refrigerant temperature sensor 19c and the third refrigerant pressure sensor 19f so that the degree of subcooling of the refrigerant on the outlet side of the chiller 16 becomes a predetermined target degree of subcooling.

[0152] In addition, controller 70 adjusts the rotational position of the valve disc of high-temperature side flow rate control valve 33 so that the high-temperature side heat medium flowing into high-temperature side flow rate control valve 33 flows out to high-temperature side radiator 34 and heater core 35. Controller 70 adjusts the rotational position of the valve disc of high-temperature side flow rate control valve 33 in accordance with the target temperature in the vehicle cabin set by the temperature setting switch, etc., to change the flow rates of the high-temperature side heat medium flowing out to high-temperature side radiator 34 and heater core 35, respectively.

[0153] Furthermore, when the second expansion valve 17b is brought into the throttling state, the control device 70 adjusts the rotational position of the valve element of the battery-side three-way valve 42 so that the low-temperature side heat medium flowing into the battery-side three-way valve 42 does not flow into the cooling water passage of the battery 60, but flows only into the low-temperature side radiator 43. Furthermore, when the second expansion valve 17b is brought into the fully closed state, the control device 70 brings the battery-side three-way valve 42 into the fully closed state.

[0154] The control device 70 then adjusts the rotational position of the valve disc of the equipment-side three-way valve 44c so that the low-temperature side heat medium flowing into the equipment-side three-way valve 44c flows out to the low-temperature side radiator 43 and the bypass passage 44d. The control device 70 adjusts the rotational position of the valve disc of the equipment-side three-way valve 44c based on a detection signal transmitted from the third low-temperature side heat medium temperature sensor 47c, thereby adjusting the flow rates of the low-temperature side heat medium flowing into the low-temperature side radiator 43 and the bypass passage 44d.

[0155] The control device 70 also operates the electric actuator of the air mix door 56 to adjust the volume of the blown air passing through the heater core 35 side and the cold air bypass passage 55 so that the temperature of the blown air blown into the vehicle compartment approaches the target blowing temperature. Furthermore, the control device 70 adjusts the heating capacity of the electric heater 32 as necessary based on a detection signal transmitted from the first high-temperature side heat medium temperature sensor 37a so that the temperature of the high-temperature side heat medium flowing out from the heater core 35 becomes equal to or higher than a predetermined reference temperature.

[0156] The control device 70 adjusts the rotation speed of the compressor 12 based on the detection signal transmitted from the second high-temperature side heat medium temperature sensor 37b. The control device 70 also outputs control signals for operating the high-temperature side heat medium pump 31, the equipment pump 44b, and the blower 53. When the second expansion valve 17b is in the throttling state, the control device 70 outputs a control signal for operating the low-temperature side heat medium pump 41, and when the second expansion valve 17b is in the fully closed state, the control device 70 does not output a control signal for operating the low-temperature side heat medium pump 41.

[0157] Therefore, in the refrigeration cycle device 10 in the dehumidification heating mode, the refrigerant circulates in the following order: compressor 12 → water-refrigerant heat exchanger 13 → refrigerant branching section 18 → first expansion valve 17a → indoor evaporator 14 → air conditioning inlet piping 11a → connection device 100 → compressor outlet piping 11c → compressor 12.

[0158] In the refrigeration cycle apparatus 10 in the dehumidifying and heating mode, when the second expansion valve 17b is in a throttled state, the refrigerant branches and flows at the refrigerant branching section 18. In this case, in the refrigeration cycle apparatus 10, the refrigerant branched at the refrigerant branching section 18 flows in the following order: second expansion valve 17b → chiller 16 → cooling section inlet pipe 11b → connection device 100 → compressor outlet pipe 11c → compressor 12.

[0159] In the refrigeration cycle apparatus 10 in the dehumidifying and heating mode, when the second expansion valve 17b is fully closed, the refrigerant does not flow through the cooling section inlet pipe 11b.

[0160] In the high-temperature side heat medium circuit 30 in the dehumidification heating mode, the high-temperature side heat medium pump 31 causes the high-temperature side heat medium flowing out of the water passage of the water-refrigerant heat exchanger 13 to flow to the high-temperature side radiator 34 and the heater core 35. The high-temperature side heat medium flowing out of the high-temperature side radiator 34 and the heater core 35 then joins at the high-temperature side heat medium junction 36 and returns to the suction port of the high-temperature side heat medium pump 31.

[0161] In the low-temperature side heat medium circuit 40 in the dehumidifying and heating mode, when the second expansion valve 17b is in the throttled state, the low-temperature side heat medium pump 41 causes the low-temperature side heat medium flowing out of the water passage of the chiller 16 to flow to the low-temperature side radiator 43 and return to the suction port of the low-temperature side heat medium pump 41. In the low-temperature side heat medium circuit 40 in the dehumidifying and heating mode, the low-temperature side heat medium flows in the order of the equipment pump 44b → the cooling water passage of the inverter 61 → the cooling water passage of the motor generator 62 → the cooling water passage of the transaxle unit 63, and then flows into the equipment side three-way valve 44c. The low-temperature side heat medium that has flowed into the equipment side three-way valve 44c then flows into the low-temperature side radiator 43 and the bypass passage 44d depending on the rotational position of the valve disc of the equipment side three-way valve 44c, and returns to the suction port of the equipment pump 44b.

[0162] Thus, in the dehumidifying and heating mode, the refrigerant flowing out from the indoor evaporator 14 flows into the connection device 100 from the rapid inlet 121 via the air conditioning inlet piping 11a. When the second expansion valve 17b is in a throttled state, the refrigerant flowing out from the chiller 16 flows into the connection device 100 from the low inlet 131 via the cooling section inlet piping 11b. On the other hand, when the second expansion valve 17b is in a fully closed state, no refrigerant flows into the connection device 100 from the low inlet 131.

[0163] The connection device 100 causes the refrigerant that has flowed in from the rapid flow inlet 121 and the low flow inlet 131 to flow out from the refrigerant outlet 143 and guides it to the compressor outlet pipe 11c.

[0164] In the refrigeration cycle apparatus 10 in the dehumidification heating mode, the water-refrigerant heat exchanger 13 heats the high-temperature side heat medium using the refrigerant discharged from the compressor 12 as a heat source, and the first expansion valve 17a reduces the pressure of the refrigerant flowing out from the water-refrigerant heat exchanger 13. In the refrigeration cycle apparatus 10, the indoor evaporator 14 absorbs heat from the blown air blown by the blower 53 to evaporate the refrigerant, thereby cooling and dehumidifying the blown air.

[0165] In the refrigeration cycle apparatus 10 in the dehumidifying heating mode, when the second expansion valve 17b is in a throttling state, the second expansion valve 17b reduces the pressure of the refrigerant flowing out from the water-refrigerant heat exchanger 13. In the refrigeration cycle apparatus 10, the chiller 16 absorbs heat from the low-temperature side heat medium flowing through the low-temperature side heat medium circuit 40 to cool the low-temperature side heat medium.

[0166] In the high-temperature side heat medium circuit 30 in the dehumidifying and heating mode, the high-temperature side radiator 34 radiates heat from the high-temperature side heat medium heated in the water-refrigerant heat exchanger 13. In the high-temperature side heat medium circuit 30 in the dehumidifying and heating mode, the high-temperature side heat medium heated by the water-refrigerant heat exchanger 13 and the electric heater 32 exchanges heat with the blown air blown from the blower 53 in the heater core 35, heating the blown air.

[0167] In the low-temperature side heat medium circuit 40 in the dehumidifying and heating mode, when the second expansion valve 17b is in the throttle state, the low-temperature side heat medium that has been heated by absorbing heat from the outside air exchanges heat with the refrigerant in the chiller 16 to heat the refrigerant, as in the heating mode. In the low-temperature side heat medium circuit 40 in the dehumidifying and heating mode, a portion of the low-temperature side heat medium heated by the self-heating of the inverter 61, the motor generator 62, and the transaxle device 63 flows into the bypass passage 44d, and the remaining flow rate flows into the low-temperature side radiator 43.

[0168] Therefore, in the vehicle air conditioner 1 in the dehumidifying and heating mode, the ventilation air is cooled and dehumidified by the interior evaporator 14 and reheated by the heater core 35, and is blown into the vehicle cabin. This allows the vehicle air conditioner 1 to perform dehumidifying and heating of the vehicle cabin.

[0169] In addition, by heating the refrigerant through heat exchange between the heated low-temperature side heat medium and the refrigerant, it is possible to heat the refrigerant circulating through the refrigeration cycle device 10. Furthermore, by circulating the low-temperature side heat medium cooled by the low-temperature side radiator 43 through the low-temperature side heat medium circuit 40, it is possible to cool or heat the inverter 61, the motor generator 62, and the transaxle device 63, respectively.

[0170] (4) Cooling mode The cooling mode is an operation mode in which the battery 60 is cooled without cooling or heating the interior of the vehicle.

[0171] In the cooling mode, the control device 70 switches the refrigeration cycle device 10 to a refrigerant circuit in the cooling mode. Specifically, the control device 70 fully closes the first expansion valve 17a and throttles the second expansion valve 17b. Based on detection signals transmitted from the third refrigerant temperature sensor 19c and the third refrigerant pressure sensor 19f, the control device 70 determines the opening degree of the second expansion valve 17b so that the degree of subcooling of the refrigerant on the outlet side of the chiller 16 becomes a predetermined target degree of subcooling.

[0172] In addition, the control device 70 adjusts the rotational position of the valve body of the high-temperature side flow rate control valve 33 so that the high-temperature side heat medium flowing into the high-temperature side flow rate control valve 33 does not flow into the heater core 35, but flows only into the high-temperature side radiator 34.

[0173] Furthermore, the control device 70 adjusts the rotational position of the valve disc of the battery-side three-way valve 42 so that the low-temperature side heat medium flowing into the battery-side three-way valve 42 flows into the coolant passage of the battery 60. The control device 70 changes the flow rate of the low-temperature side heat medium flowing into the coolant passage of the battery 60 by adjusting the rotational position of the valve disc of the battery-side three-way valve 42 based on a detection signal transmitted from the first low-temperature side heat medium temperature sensor 47a.

[0174] The control device 70 then adjusts the rotational position of the valve disc of the equipment-side three-way valve 44c so that the low-temperature side heat medium flowing into the equipment-side three-way valve 44c does not flow into the bypass passage 44d, but flows only into the low-temperature side radiator 43. The control device 70 also outputs control signals to operate the compressor 12, the high-temperature side heat medium pump 31, the low-temperature side heat medium pump 41, and the equipment pump 44b.

[0175] Therefore, in the refrigeration cycle apparatus 10 in the cooling mode, the refrigerant circulates in the following order: compressor 12 → water-refrigerant heat exchanger 13 → refrigerant branching section 18 → second expansion valve 17b → chiller 16 → cooling section inlet pipe 11b → connection device 100 → compressor outlet pipe 11c → compressor 12. In the refrigeration cycle apparatus 10 in the cooling mode, the first expansion valve 17a is fully closed, so that the refrigerant does not flow into the air conditioning inlet pipe 11a.

[0176] In the high-temperature side heat medium circuit 30 in the cooling mode, the high-temperature side heat medium pump 31 causes the high-temperature side heat medium flowing out of the water passage of the water-refrigerant heat exchanger 13 to flow to the high-temperature side radiator 34 and return to the suction port of the high-temperature side heat medium pump 31.

[0177] In the low-temperature side heat medium circuit 40 in the cooling mode, the low-temperature side heat medium pump 41 causes the low-temperature side heat medium flowing out of the water passage of the chiller 16 to flow into the coolant passage of the battery 60 and return to the suction port of the low-temperature side heat medium pump 41. In the low-temperature side heat medium circuit 40 in the cooling mode, the low-temperature side heat medium circulates in the following order: equipment pump 44b → coolant passage of the inverter 61 → coolant passage of the motor generator 62 → coolant passage of the transaxle unit 63 → low-temperature side radiator 43 → equipment pump 44b.

[0178] Thus, in the cooling mode, the refrigerant flowing out from the chiller 16 flows into the connection device 100 from the low inlet 131 via the cooling unit inlet piping 11b, but does not flow into the connection device 100 from the rapid inlet 121. Then, the connection device 100 causes the refrigerant that has flowed in from the low inlet 131 to flow out from the refrigerant outlet 143 and guides it to the compressor outlet piping 11c.

[0179] In the refrigeration cycle apparatus 10 in the cooling mode, the water-refrigerant heat exchanger 13 heats the high-temperature side heat medium using the refrigerant discharged from the compressor 12 as a heat source, and the second expansion valve 17b reduces the pressure of the refrigerant flowing out from the water-refrigerant heat exchanger 13. In the refrigeration cycle apparatus 10, the chiller 16 absorbs heat from the low-temperature side heat medium flowing through the low-temperature side heat medium circuit 40 to evaporate the refrigerant and cool the low-temperature side heat medium.

[0180] In the high-temperature side heat medium circuit 30 in the cooling mode, the high-temperature side radiator 34 dissipates heat from the high-temperature side heat medium heated in the water-refrigerant heat exchanger 13. In the low-temperature side heat medium circuit 40 in the cooling mode, the low-temperature side heat medium cooled in the chiller 16 absorbs heat from the battery 60 in the coolant passage of the battery 60. In the low-temperature side heat medium circuit 40 in the cooling mode, the low-temperature side radiator 43 dissipates heat from the low-temperature side heat medium heated by the heat generated by the inverter 61, the motor generator 62, and the transaxle device 63.

[0181] Therefore, in the vehicle air conditioner 1 in the cooling mode, the low-temperature side heat medium cooled by the chiller 16 is circulated through the coolant passage of the battery 60 to cool the battery 60. Also, in the vehicle air conditioner 1 in the cooling mode, the low-temperature side heat medium cooled by the low-temperature side radiator 43 is circulated through the low-temperature side heat medium circuit 40 to cool the inverter 61, the motor generator 62, and the transaxle device 63.

[0182] Incidentally, when operating in each of the above-mentioned air conditioning modes, the vehicle air conditioner 1 of this embodiment can execute an operation mode in which each air conditioning mode is combined with a cooling mode under an operating condition that requires cooling of the battery 60. An operating condition that requires cooling of the battery 60 is, for example, a case in which the temperature of the battery 60 becomes higher than a predetermined battery reference temperature due to the operation of the battery 60.

[0183] The following describes an example of an operation mode in which the air conditioning mode and the cooling mode are combined, in which the air conditioning mode and the cooling mode are combined. Note that the vehicle air conditioner 1 of this embodiment can also operate in an operation mode in which the heating mode and the cooling mode are combined, and an operation mode in which the dehumidification heating mode and the cooling mode are combined.

[0184] (5) Cooling mode The air-conditioning cooling mode is an operation mode in which the interior of the vehicle is cooled and the battery 60 is cooled.

[0185] In the cooling / cooling mode, the control device 70 switches the refrigeration cycle device 10 to a refrigerant circuit for the cooling / cooling mode. Specifically, the control device 70 throttles the first expansion valve 17a and the second expansion valve 17b.

[0186] The control device 70 determines the opening degree of the first expansion valve 17a based on detection signals transmitted from the second refrigerant temperature sensor 19b and the second refrigerant pressure sensor 19e so that the degree of superheat of the refrigerant on the outlet side of the indoor evaporator 14 becomes a predetermined target degree of superheat. The control device 70 also determines the opening degree of the second expansion valve 17b based on detection signals transmitted from the third refrigerant temperature sensor 19c and the third refrigerant pressure sensor 19f so that the degree of subcooling of the refrigerant on the outlet side of the chiller 16 becomes a predetermined target degree of subcooling.

[0187] In addition, the control device 70 adjusts the rotational position of the valve body of the high-temperature side flow rate control valve 33 so that the high-temperature side heat medium flowing into the high-temperature side flow rate control valve 33 does not flow into the heater core 35, but flows only into the high-temperature side radiator 34.

[0188] Furthermore, the control device 70 adjusts the rotational position of the valve disc of the battery-side three-way valve 42 so that the low-temperature side heat medium flowing into the battery-side three-way valve 42 flows into the coolant passage of the battery 60. The control device 70 changes the flow rate of the low-temperature side heat medium flowing into the coolant passage of the battery 60 by adjusting the rotational position of the valve disc of the battery-side three-way valve 42 based on a detection signal transmitted from the first low-temperature side heat medium temperature sensor 47a.

[0189] The controller 70 adjusts the rotational position of the valve element of the equipment side three-way valve 44c so that the low-temperature side heat medium flowing into the equipment side three-way valve 44c flows only to the low-temperature side radiator 43 without flowing into the bypass passage 44d.

[0190] The control device 70 also operates the electric actuator of the air mix door 56 so that the entire amount of the blown air that has passed through the indoor evaporator 14 passes through the cold air bypass passage 55. Then, the control device 70 outputs control signals to operate the compressor 12, the high-temperature side heat medium pump 31, the low-temperature side heat medium pump 41, the equipment pump 44b, and the blower 53.

[0191] Therefore, in the refrigeration cycle apparatus 10 in the cooling / cooling mode, the refrigerant flows in the order of the compressor 12, the water-refrigerant heat exchanger 13, and the refrigerant branching section 18, and is branched at the refrigerant branching section 18. One of the refrigerants branched at the refrigerant branching section 18 flows in the order of the first expansion valve 17a, the indoor evaporator 14, the air conditioning inlet pipe 11a, the connection device 100, the compressor outlet pipe 11c, and the compressor 12. The other refrigerant branched at the refrigerant branching section 18 flows in the order of the second expansion valve 17b, the chiller 16, the cooling section inlet pipe 11b, the connection device 100, the compressor outlet pipe 11c, and the compressor 12.

[0192] In the high-temperature side heat medium circuit 30 in the air-conditioning cooling mode, the high-temperature side heat medium pump 31 causes the high-temperature side heat medium flowing out of the water passage of the water-refrigerant heat exchanger 13 to flow to the high-temperature side radiator 34 and return to the suction side of the high-temperature side heat medium pump 31.

[0193] In the low-temperature side heat medium circuit 40 in the air-conditioning / cooling mode, the low-temperature side heat medium pump 41 causes the low-temperature side heat medium flowing out of the water passage of the chiller 16 to flow into the coolant passage of the battery 60 and return to the suction port of the low-temperature side heat medium pump 41. In the low-temperature side heat medium circuit 40 in the air-conditioning / cooling mode, the low-temperature side heat medium circulates in the following order: equipment pump 44b → coolant passage of the inverter 61 → coolant passage of the motor generator 62 → coolant passage of the transaxle unit 63 → low-temperature side radiator 43 → equipment pump 44b.

[0194] Thus, in the air-conditioning cooling mode, the refrigerant flowing out from the indoor evaporator 14 flows into the connection device 100 from the rapid flow inlet 121 via the air-conditioning inlet piping 11a. Furthermore, the refrigerant flowing out from the chiller 16 flows into the connection device 100 from the low flow inlet 131 via the cooling unit inlet piping 11b. Then, the connection device 100 causes the refrigerant that has flowed in from the rapid flow inlet 121 and the low flow inlet 131 to flow out from the refrigerant outlet 143 and guide it to the compressor outlet piping 11c.

[0195] In the refrigeration cycle apparatus 10 in the cooling / cooling mode, the water-refrigerant heat exchanger 13 heats the high-temperature side heat medium using the refrigerant discharged from the compressor 12 as a heat source, and the first expansion valve 17a and the second expansion valve 17b reduce the pressure of the refrigerant flowing out of the water-refrigerant heat exchanger 13. In the refrigeration cycle apparatus 10, the indoor evaporator 14 absorbs heat from the blown air blown from the blower 53 to evaporate the refrigerant and cool the blown air. In the refrigeration cycle apparatus 10, the chiller 16 absorbs heat from the low-temperature side heat medium flowing through the low-temperature side heat medium circuit 40 to evaporate the refrigerant and cool the low-temperature side heat medium.

[0196] In the high-temperature side heat medium circuit 30 in the cooling mode, the high-temperature side radiator 34 dissipates heat from the high-temperature side heat medium heated in the water-refrigerant heat exchanger 13.

[0197] In the low-temperature side heat medium circuit 40 in the air-conditioning mode, the low-temperature side heat medium cooled by the chiller 16 absorbs heat from the battery 60 in the coolant passage of the battery 60. Furthermore, in the low-temperature side heat medium circuit 40 in the cooling mode, the low-temperature side radiator 43 dissipates heat from the low-temperature side heat medium heated by the heat generated by the inverter 61, the motor generator 62, and the transaxle device 63.

[0198] Therefore, in the vehicle air conditioner 1 in the cooling mode, the blown air cooled by the interior evaporator 14 is blown into the vehicle compartment, thereby cooling the vehicle compartment. Furthermore, the low-temperature side heat medium cooled by the chiller 16 is circulated through the coolant passage of the battery 60, thereby cooling the battery 60. In the vehicle air conditioner 1 in the cooling mode, the low-temperature side heat medium cooled by the low-temperature side radiator 43 is circulated through the low-temperature side heat medium circuit 40, thereby cooling the inverter 61, the motor generator 62, and the transaxle device 63.

[0199] Next, the details of the connection device 100 will be described with reference to Figs. 3 to 11. Here, the arrows indicating up and down shown in Fig. 3 indicate an up-down direction DR1 based on the direction of gravity in a situation where the connection device 100 is being used. Also, the arrows indicating front and back and left and right shown in Fig. 3 indicate a front-rear direction DR2 and a left-right direction DR3 based on a direction conveniently determined as the front in the connection device 100. Note that the up-down direction DR1 does not limit the posture of the connection device 100 in a situation where the connection device 100 is not actually used, such as during manufacture, sale, or transportation. Also, the front-rear direction DR2 and the left-right direction DR3 do not limit the posture of the connection device 100. And Fig. 4 shows the cross-sectional shape of a plane that passes through the center of the connection device 100 in the front-rear direction DR2 and is perpendicular to the front-rear direction DR2.

[0200] As shown in Figures 3 and 4, the connection device 100 includes a housing 110, and a steep upward flow path section 120, a low upward flow path section 130, and a downstream side flow path section 140, which are refrigerant passages formed inside the housing 110.

[0201] The housing 110 has a pentagonal prism shape that extends in the front-rear direction DR2 and has a pentagonal cross-sectional shape of a surface perpendicular to the front-rear direction DR2, and is made of, for example, a resin material. The housing 110 has a bottom surface portion 111 provided on the lower side in the up-down direction DR1, and a right side surface portion 112 and a left side surface portion 113 that extend upward along the up-down direction DR1 from both side ends of the bottom surface portion 111 in the left-right direction DR3.

[0202] Furthermore, the housing 110 has a right slope portion 114 that slopes from an upper end to the left in the left-right direction DR3 and extends upward in the up-down direction DR1 among the ends of the right side surface portion 112 in the up-down direction DR1. Also, the housing 110 has a left slope portion 115 that slopes from an upper end to the right in the left-right direction DR3 and extends upward in the up-down direction DR1 among the ends of the left side surface portion 113 in the up-down direction DR1.

[0203] In the cross-sectional shape of a plane perpendicular to the front-rear direction DR2, the right slope portion 114 and the left slope portion 115 are symmetrical with respect to a straight line that passes through the center of the bottom surface portion 111 in the left-right direction DR3 and extends along the up-down direction DR1, and have the same inclination angle. In addition, the end portion of the right slope portion 114 opposite to the side where the right side surface portion 112 is connected is connected to the end portion of the left slope portion 115 opposite to the side where the left side surface portion 113 is connected. The housing 110 may be made of a metal material such as aluminum.

[0204] 4, a steep upward flow path section 120 is formed inside the housing 110, extending from the surface of the right slope section 114 toward the bottom surface section 111 without penetrating all the way to the bottom surface section 111. Also, a low upward flow path section 130 is formed inside the housing 110, extending from the surface of the left slope section 115 toward the right side surface section 112 without penetrating all the way to the right side surface section 112. Also, a downstream side flow path section 140 is formed inside the housing 110, extending from the surface of the bottom surface section 111 toward the upper side in the up-down direction DR1 to the right slope section 114 and the left slope section 115 without penetrating all the way.

[0205] The steep upward flow path section 120 extends from a portion of the surface of the right slope section 114 that is above the center in the up-down direction DR1 toward a portion to the left of the center in the left-right direction DR3 of the bottom surface section 111. Furthermore, of both ends of the steep upward flow path section 120, ends opposite to the side positioned on the surface of the right slope section 114 are connected to ends of both ends of the downstream side flow path section 140 opposite to the side positioned on the surface of the bottom surface section 111. That is, of the steep upward flow path section 120, an upper end of the downstream side flow path section 140 in the up-down direction DR1 is connected to a lower end of the steep upward flow path section 120 in the up-down direction DR1.

[0206] The low upper flow path section 130 extends from a portion of the surface of the left inclined surface section 115 that is below the center in the vertical direction DR1 toward a portion of the right side surface section 112 that is below the center in the vertical direction DR1. In addition, of both ends of the low upper flow path section 130, a portion in the middle of the refrigerant passage different from both ends of the downstream flow path section 140 is connected to an end opposite to the side positioned on the surface of the left inclined surface section 115. That is, in the low upper flow path section 130, a portion between an upper end and a lower end of the downstream flow path section 140 in the vertical direction DR1 is connected to a lower end of the low upper flow path section 130 in the vertical direction DR1.

[0207] The steep ascending flow path section 120 and the low upstream flow path section 130 are not directly connected to each other, but are connected via the downstream side flow path section 140. For this reason, the refrigerant flowing through the low upstream flow path section 130 does not directly merge with the refrigerant flowing through the steep ascending flow path section 120. In this embodiment, the steep ascending flow path section 120 functions as a first inclined upstream side flow path section, and the low upstream flow path section 130 functions as a second inclined upstream side flow path section.

[0208] The steep upward flow path section 120 forms a refrigerant passage for guiding the refrigerant flowing out from the air conditioning inlet pipe 11a into the inside of the housing 110, and is connected one-to-one to the air conditioning inlet pipe 11a. The steep upward flow path section 120 has a steep inlet 121 on the upstream side of the refrigerant flow that allows the refrigerant to flow into the steep upward flow path section 120, and has a steep junction port 122 on the downstream side of the refrigerant flow that communicates with the downstream side flow path section 140.

[0209] Furthermore, the steep upward flow path section 120 extends linearly in a direction different from the direction in which the downstream side flow path section 140 extends. The direction in which the steep upward flow path section 120 extends will be described later.

[0210] The steep upward flow path section 120 is formed so that the first inner diameter φ1, which is the inner diameter of the steep upward flow path section 120, is slightly larger than the outer diameter of the air conditioning inlet pipe 11a, and is formed so that the air conditioning inlet pipe 11a can be inserted into the inside of the steep upward flow path section 120 from the steep inlet 121.

[0211] The steep upward flow passage section 120 is formed so that the first inner diameter φ1 is uniform from the upstream side of the refrigerant flow to the downstream side of the refrigerant flow. The first inner diameter φ1 is the diameter of a cross-sectional shape in a direction perpendicular to the direction in which the steep upward flow passage section 120 extends.

[0212] The low upstream flow path section 130 forms a refrigerant passage for guiding the refrigerant flowing out from the cooling unit inlet pipe 11b into the housing 110, and is connected one-to-one to the cooling unit inlet pipe 11b. The low upstream flow path section 130 has a low inlet port 131 that allows the refrigerant to flow into the low upstream flow path section 130 on the upstream side of the refrigerant flow, and a low junction port 132 that communicates with the downstream side flow path section 140 on the downstream side of the refrigerant flow.

[0213] The low upstream flow passage section 130 extends linearly in a direction different from the direction in which the downstream side flow passage section 140 extends and the direction in which the steep upstream flow passage section 120 extends. The direction in which the low upstream flow passage section 130 extends will be described later.

[0214] The low upper flow path section 130 is formed so that the second inner diameter φ2, which is the inner diameter of the low upper flow path section 130, is slightly larger than the outer diameter of the cooling section inlet piping 11b, and is formed so that the cooling section inlet piping 11b can be inserted into the inside of the low upper flow path section 130 from the low inlet 131.

[0215] The low upper flow passage section 130 is formed so that the second inner diameter φ2 is equal from the upstream side of the refrigerant flow to the downstream side of the refrigerant flow. The second inner diameter φ2 is a diameter of a cross-sectional shape in a direction perpendicular to the extension direction of the low upper flow passage section 130. In this embodiment, the first inner diameter φ1 and the second inner diameter φ2 are formed to be equal to each other.

[0216] The downstream flow path section 140 forms a refrigerant passage for allowing the refrigerant that has flowed into the inside of the housing 110 via the steep upward flow path section 120 and the low upward flow path section 130 to flow out of the housing 110. The downstream flow path section 140 is connected one-to-one to the compressor outflow pipe 11c.

[0217] The downstream flow passage section 140 has a first junction section 141 on the upstream side of the refrigerant flow, which merges the refrigerant flowing through the fast upstream flow passage section 120 into the downstream flow passage section 140. The downstream flow passage section 140 also has a second junction section 142 on the downstream side of the refrigerant flow of the first junction section 141, which merges the refrigerant flowing through the low upstream flow passage section 130 into the downstream flow passage section 140. The downstream flow passage section 140 also has a refrigerant outlet 143, into which the compressor outlet pipe 11c is inserted, on the most downstream side of the refrigerant flow.

[0218] The downstream flow path section 140 extends linearly along the up-down direction DR1 from approximately the center of the surface of the bottom surface section 111 toward a portion where the right inclined surface section 114 and the left inclined surface section 115 are connected. That is, the direction in which the downstream flow path section 140 of this embodiment extends is along the up-down direction DR1, excluding the left-right direction DR3 and the front-rear direction DR2.

[0219] Here, a portion where a straight line L1 that passes through the center of the refrigerant outlet 143 and extends in the direction in which the downstream flow path section 140 extends and a straight line L2 that passes through the center of the rapid inlet 121 and extends in the direction in which the rapid upward flow path section 120 extends intersect is defined as a first junction 141. A portion where a straight line L1 that passes through the center of the refrigerant outlet 143 and extends in the direction in which the downstream flow path section 140 extends and a straight line L3 that passes through the center of the low inlet 131 and extends in the direction in which the low upward flow path section 130 extends intersect is defined as a second junction 142.

[0220] In this embodiment, the first junction 141 and the second junction 142 are provided at different positions in the downstream passage section 140. Specifically, the first junction 141 is provided at a position upstream of the second junction 142 in the refrigerant flow in the downstream passage section 140. The first junction 141 is a portion into which the refrigerant flowing through the steep upward passage section 120 flows.

[0221] The second junction 142 is a portion into which the refrigerant that has flowed into the downstream channel section 140 from the steep upstream channel section 120 via the first junction 141 and the refrigerant that flows into the downstream channel section 140 from the low upstream channel section 130 flow. In this embodiment, the first junction 141 and the second junction 142 function as junctions.

[0222] Furthermore, the downstream flow passage section 140 has a refrigerant outlet 143, which is the most downstream side of the refrigerant flow, located at a position lower in the up-down direction DR1 than the rapid inlet 121, which is the most upstream side of the refrigerant flow of the rapid upward flow passage section 120. Furthermore, the downstream flow passage section 140 has a refrigerant outlet 143, which is located at a position lower in the up-down direction DR1 than the low inlet 131, which is the most upstream side of the refrigerant flow of the low upward flow passage section 130. In other words, the refrigerant outlet 143 is positioned vertically lower than the rapid inlet 121 and the low inlet 131.

[0223] Refrigerant outlet 143 is formed in bottom portion 111 so that the opening direction faces vertically downward. When connection device 100 is applied to vehicle air conditioner 1, connection device 100 is disposed in a position where refrigerant outlet 143 is vertically above refrigerant suction port 12a of compressor 12, as shown in FIG.

[0224] The downstream flow passage section 140 is formed so that the third inner diameter φ3, which is the inner diameter of the downstream flow passage section 140, is slightly larger than the outer diameter of the compressor outflow piping 11c, and is formed so that the compressor outflow piping 11c can be inserted into the inside of the downstream flow passage section 140 from the refrigerant outlet 143.

[0225] The downstream flow passage section 140 is formed so that the third inner diameter φ3 is uniform from the first junction section 141 through the second junction section 142 to the refrigerant outlet 143. The third inner diameter φ3 is a diameter in a cross section perpendicular to the direction in which the downstream flow passage section 140 extends. The third inner diameter φ3 is formed larger than the first inner diameter φ1 and the second inner diameter φ2. That is, the downstream flow passage section 140 is formed so that the inner diameter on the refrigerant flow downstream side of the first junction section 141 is larger than the first inner diameter φ1, and the inner diameter on the refrigerant flow downstream side of the second junction section 142 is larger than the second inner diameter φ2.

[0226] In other words, the downstream flow passage section 140, downstream of the first junction 141 in the refrigerant flow, has a larger flow passage cross-sectional area in a cross section perpendicular to the refrigerant flow direction than the steep upward flow passage section 120. Also, the downstream flow passage section 140, downstream of the second junction 142, has a larger flow passage cross-sectional area in a cross section perpendicular to the refrigerant flow direction than the low upward flow passage section 130.

[0227] Here, the ratio of the inner diameter of the downstream side flow passage section 140 to the inner diameter of the steep upward flow passage section 120 and the inner diameter of the low upward flow passage section 130 will be described with reference to the graph of Fig. 6. The pressure loss when the refrigerant passes through the connection device 100 and the manufacturing cost of the connection device 100 vary depending on the ratio of the inner diameter of the downstream side flow passage section 140 to the inner diameter of the steep upward flow passage section 120 and the inner diameter of the low upward flow passage section 130. As described above, in this embodiment, the inner diameter of the steep upward flow passage section 120 is the first inner diameter φ1, the inner diameter of the low upward flow passage section 130 is the second inner diameter φ2, and the inner diameter of the downstream side flow passage section 140 is the third inner diameter φ3.

[0228] The connection device 100 has a third inner diameter φ3 larger than the first inner diameter φ1 and the second inner diameter φ2. The speed of the refrigerant flowing through the downstream flow passage section 140 decreases as the inner diameter of the downstream flow passage section 140 increases. Therefore, when the inner diameter of the downstream flow passage section 140 is larger than the first inner diameter φ1 and the second inner diameter φ2, the speed of the refrigerant flowing through the downstream flow passage section 140 is slower than when the inner diameter of the downstream flow passage section 140 is equal to the first inner diameter φ1 and the second inner diameter φ2. The speed of the refrigerant flowing through the downstream flow passage section 140 decreases as the third inner diameter φ3 is larger than the first inner diameter φ1 and the second inner diameter φ2.

[0229] In other words, the speed of the refrigerant flowing through the downstream channel portion 140 decreases as the ratio of the third inner diameter φ3 to the first inner diameter φ1 and the second inner diameter φ2 increases.

[0230] Furthermore, the pressure loss caused by the refrigerant flowing through the downstream flow path section 140 decreases as the speed of the refrigerant flowing through the downstream flow path section 140 decreases. Therefore, as shown in Fig. 6, the pressure loss caused inside the connection device 100 decreases as the ratio of the third inner diameter φ3 to the first inner diameter φ1 and the second inner diameter φ2 increases. Hereinafter, the ratio of the third inner diameter φ3 to the first inner diameter φ1 and the second inner diameter φ2 is also referred to as the connection portion diameter ratio σ.

[0231] On the other hand, from the viewpoint of the manufacturing cost of the connection device 100, it is most desirable to form the steep upward flow path section 120 and the low upward flow path section 130 and the downstream side flow path section 140 with the same inner diameter when forming the refrigerant passages inside the connection device 100. This is because, in order to form the steep upward flow path section 120 and the low upward flow path section 130 and the downstream side flow path section 140 with different inner diameters, for example, tools or the like for forming refrigerant passages of different sizes are required, which is a factor in increasing the manufacturing cost.

[0232] 6, the manufacturing cost of connection device 100 is minimized when all the inner diameters from the refrigerant inlet side to the refrigerant outlet side of connection device 100 are made equal so that the value of the connection portion diameter ratio σ is 1. That is, when the first inner diameter φ1, the second inner diameter φ2, and the third inner diameter φ3 are equal to each other, the manufacturing cost of connection device 100 is minimized.

[0233] However, in this embodiment, the compressor outlet pipe 11c has a larger outer diameter than the air conditioning inlet pipe 11a and the cooling unit inlet pipe 11b as described above. Therefore, if the first inner diameter φ1, the second inner diameter φ2, and the third inner diameter φ3 are all equal in size, a refrigerant pipe conversion member having different outer diameters on the inlet side and the outlet side must be attached to the refrigerant outlet 143 in order to connect the compressor outlet pipe 11c to the refrigerant outlet 143. This is not preferable because it increases the manufacturing cost of the connection device 100 if the manufacturing cost of the connection device 100 includes the installation of the refrigerant pipe conversion member.

[0234] In contrast, it is assumed that the inner diameter of the steep upward flow path section 120 corresponds to the outer diameter of the air conditioning inlet pipe 11a, the inner diameter of the low upward flow path section 130 corresponds to the outer diameter of the cooling section inlet pipe 11b, and the inner diameter of the downstream side flow path section 140 corresponds to the outer diameter of the compressor outlet pipe 11c. In this case, although there is a factor of increased manufacturing costs due to forming refrigerant passages with different inner diameters, since measures such as the installation of a refrigerant pipe conversion member are not required, an increase in the manufacturing cost of the connection device 100 as a whole can be relatively suppressed.

[0235] For this reason, in this embodiment, the inner diameter of the steep upward flow path section 120, i.e., the first inner diameter φ1, is formed to a size corresponding to the outer diameter of the air conditioning inlet pipe 11a. Specifically, the inner diameter of the steep upward flow path section 120 is formed slightly larger than the outer diameter 15.88 mm of the air conditioning inlet pipe 11a so that the air conditioning inlet pipe 11a can be inserted therein. In other words, the inner diameter of the portion of the steep upward flow path section 120 to which the air conditioning inlet pipe 11a is connected is formed to a size corresponding to the most downstream portion of the refrigerant flow of the air conditioning inlet pipe 11a.

[0236] The inner diameter of the low upstream flow path section 130, i.e., the second inner diameter φ2, is formed to a size corresponding to the outer diameter of the cooling section inlet pipe 11b so that the cooling section inlet pipe 11b can be inserted. Specifically, the inner diameter of the low upstream flow path section 130 is formed slightly larger than the outer diameter 15.88 mm of the cooling section inlet pipe 11b. In other words, the inner diameter of the portion of the low upstream flow path section 130 to which the cooling section inlet pipe 11b is connected is formed to a size corresponding to the downstreammost portion of the refrigerant flow of the cooling section inlet pipe 11b.

[0237] The inner diameter of the downstream flow passage section 140, i.e., the third inner diameter φ3, is formed to a size corresponding to the outer diameter of the compressor outlet pipe 11c. Specifically, the inner diameter of the downstream flow passage section 140 is formed slightly larger than the outer diameter 19.05 mm of the compressor outlet pipe 11c so that the compressor outlet pipe 11c can be inserted. In other words, the inner diameter of the portion of the downstream flow passage section 140 to which the compressor outlet pipe 11c is connected is formed to a size corresponding to the most upstream portion of the refrigerant flow of the compressor outlet pipe 11c. The value of the connection diameter ratio σ in this embodiment determined in this manner is 1.20.

[0238] 6, the manufacturing cost of the connection device 100 increases as the connection diameter ratio σ becomes larger than 1, but the increase in manufacturing cost can be relatively suppressed when the connection diameter ratio σ is equal to or less than 1.20. In the range of the connection diameter ratio σ between 1 and 1.20, the increase in manufacturing cost due to the increase in the connection diameter ratio σ is smaller than the decrease in pressure loss due to the increase in the connection diameter ratio σ.

[0239] Therefore, as in this embodiment, by setting the first inner diameter φ1, the second inner diameter φ2, and the third inner diameter φ3 so that the connection portion diameter ratio σ is approximately 1.20, it is possible to suppress pressure loss while relatively reducing the manufacturing costs of the connection device 100.

[0240] Also, suppose that the inner diameter of the downstream flow passage portion 140 is made larger than the outer diameter of the compressor outlet pipe 11c in order to make the value of the connection portion diameter ratio σ larger than 1.20. In this case, in order to manufacture the connection device 100, in addition to the increase in manufacturing costs due to the formation of refrigerant passages with different inner diameters inside the connection device 100, measures such as the installation of a refrigerant pipe conversion member for connecting the compressor outlet pipe 11c to the refrigerant outlet 143 are also required.

[0241] Therefore, the manufacturing cost of the connection device 100 increases rapidly when the value of the connection diameter ratio σ is greater than 1.20. In other words, when the first inner diameter φ1 corresponds to the outer diameter of the air conditioning inlet pipe 11a and the second inner diameter φ2 corresponds to the outer diameter of the cooling section inlet pipe 11b, the manufacturing cost increases as the third inner diameter φ3 becomes larger than the size corresponding to the outer diameter of the compressor outlet pipe 11c. In addition, in a range where the value of the connection diameter ratio σ is greater than 1.20, the increase in manufacturing cost with an increase in the connection diameter ratio σ is far greater than the decrease in pressure loss with an increase in the connection diameter ratio σ.

[0242] Therefore, when the first inner diameter φ1 corresponds to the outer diameter of the air conditioning inlet pipe 11a and the second inner diameter φ2 corresponds to the outer diameter of the cooling section inlet pipe 11b, it is desirable to set the third inner diameter φ3 so that the value of the connection section diameter ratio σ is approximately 1.20.

[0243] Next, the direction in which the steep upward flow passage section 120 and the low upward flow passage section 130 extend will be described in detail using the direction in which the downstream flow passage section 140 extends. Here, the direction along the vertical direction DR1 extending from the first junction section 141 and the second junction section 142 toward the downstream side of the refrigerant flow of the downstream flow passage section 140 is defined as the downstream direction, and the direction opposite to the downstream direction is defined as a predetermined junction reference direction DRC. The predetermined junction reference direction DRC is a direction toward the upper side along the vertical direction DR1 with the first junction section 141 and the second junction section 142 as references.

[0244] As shown in Fig. 4, the steep upward flow passage section 120 extends at a first angle θ1 greater than 0° and smaller than 90° with respect to a predetermined junction reference direction DRC with respect to the first junction section 141 as a reference. Here, the angle extending from the first junction section 141 with respect to the predetermined junction reference direction DRC is an angle in which the upper side of the vertical direction DR1 is set to 0° and the clockwise direction is set to the positive direction in the cross-sectional view shown in Fig. 4. The first angle θ1 is an angle formed by the predetermined junction reference direction DRC and the direction in which the steep upward flow passage section 120 extends with the first junction section 141 as the center.

[0245] In this embodiment, the steep upward flow path section 120 extends so that the first angle θ1 is greater than 0° and less than 90° (30° in this embodiment). Thus, the steep upward flow path section 120 extends from the first junction section 141 upward in the vertical direction DR1 and to the right in the horizontal direction DR3, shifted by 30° from a predetermined junction reference direction DRC. The direction in which the steep upward flow path section 120 extends includes the horizontal direction DR3 and the vertical direction DR1, but does not include the front-rear direction DR2.

[0246] The steep upward flow passage section 120 may be configured such that the first angle θ1 is greater than 30° (e.g., 80°) or less than 30° (e.g., 20°). However, it is preferable that the first angle θ1 is as small as possible between 0° and 90°. For example, it is preferable that the first angle θ1 is 65° or less. More specifically, it is preferable that the first angle θ1 is 45° or less.

[0247] In contrast, the low upper flow passage section 130 extends at a second angle θ2 greater than 0° and smaller than 90° with respect to a predetermined junction reference direction DRC with the second junction section 142 as a reference. Here, the angle extending from the second junction section 142 with respect to the predetermined junction reference direction DRC is an angle in which the upper side of the vertical direction DR1 is set to 0° and the counterclockwise direction is the positive direction in the cross-sectional view shown in Fig. 4. The second angle θ2 is an angle formed by the predetermined junction reference direction DRC and the direction in which the low upper flow passage section 130 extends with the second junction section 142 as the center.

[0248] In this embodiment, the low upper flow path section 130 extends so that the second angle θ2 is greater than 0° and less than 90°, and is greater than the first angle θ1 (60° in this embodiment). Thus, the low upper flow path section 130 extends from the second junction section 142 toward the upper side in the vertical direction DR1 and toward the left side in the horizontal direction DR3, shifted by 60° from a predetermined junction reference direction DRC. The direction in which the low upper flow path section 130 extends includes the horizontal direction DR3 and the vertical direction DR1, but does not include the front-rear direction DR2.

[0249] The low upstream flow path section 130 may be configured such that the second angle θ2 is greater than 60° (e.g., 85°) or less than 60° (e.g., 50°) as long as it is greater than the first angle θ1. However, it is preferable that the second angle θ2 is as small as possible between 0° and 90°. For example, it is preferable that the second angle θ2 is 80° or less. More specifically, it is preferable that the second angle θ2 is 70° or less.

[0250] The angle formed by the straight lines L1 and L2 is the sum of the first angle θ1 and the second angle θ2. The angle formed by the straight lines L1 and L2 is smaller than the first angle θ1 and the second angle θ2.

[0251] Next, in the connection device 100 having the above configuration, the flow of the refrigerant flowing inside the housing 110 when the refrigeration cycle apparatus 10 operates in each operation mode will be described with reference to FIGS.

[0252] As described above, in the cooling mode, the refrigerant flows into the connection device 100 from the rapid flow inlet 121 via the air conditioning inlet piping 11a, but the refrigerant does not flow into the connection device 100 from the low flow inlet 131. Also, in the dehumidification heating mode, when the second expansion valve 17b is fully closed, the refrigerant flows into the connection device 100 from the rapid flow inlet 121 via the air conditioning inlet piping 11a, but the refrigerant does not flow into the connection device 100 from the low flow inlet 131.

[0253] 7, the refrigerant flowing in from the rapid flow inlet 121 flows along the direction in which the rapid upward flow passage section 120 extends, and the flow direction of the refrigerant is changed by 30° when the refrigerant flows into the downstream flow passage section 140 from the rapid junction port 122. The refrigerant that flows into the downstream flow passage section 140 flows along the direction in which the downstream flow passage section 140 extends, and flows out from the refrigerant outlet 143 to the compressor outflow pipe 11c.

[0254] In addition, in the heating mode and the cooling mode, the refrigerant flows into the connection device 100 from the low inlet 131 via the cooling section inlet pipe 11b, but the refrigerant does not flow into the connection device 100 from the rapid inlet 121. The refrigerant that flows into the connection device 100 from the low inlet 131 flows along the direction in which the low upstream flow passage section 130 extends, as shown by the refrigerant flow F2 in Fig. 8, and when the refrigerant flows into the downstream flow passage section 140 from the low junction port 132, the flow direction of the refrigerant is changed by 60°. The refrigerant that flows into the downstream flow passage section 140 flows along the direction in which the downstream flow passage section 140 extends, and flows out from the refrigerant outlet 143 to the compressor outlet pipe 11c.

[0255] In the air-conditioning cooling mode, the refrigerant flows into the connection device 100 from the rapid inlet 121 via the air-conditioning inlet piping 11a, and also flows into the connection device 100 from the low inlet 131 via the cooling unit inlet piping 11b. In the dehumidifying heating mode, when the second expansion valve 17b is in the throttled state, the refrigerant flows into the connection device 100 from the rapid inlet 121 via the air-conditioning inlet piping 11a, and also flows into the connection device 100 from the low inlet 131 via the cooling unit inlet piping 11b.

[0256] The refrigerant flowing in from the rapid inlet 121 flows along the direction in which the rapid upward flow path section 120 extends, as indicated by the refrigerant flow F3 in Fig. 9. The flow velocity vector of the refrigerant flowing along the direction in which the rapid upward flow path section 120 extends has a downward flow velocity vector component in the up-down direction DR1 and a leftward flow velocity vector component in the left-right direction DR3. The flow velocity vector of the refrigerant indicates the speed vector of the refrigerant flow.

[0257] When the refrigerant flowing through the steep upward flow passage section 120 flows into the downstream flow passage section 140 from the steep junction port 122, the refrigerant flow direction is changed by 30° without colliding with the refrigerant flowing in from the low junction port 132.

[0258] 9, the refrigerant flowing in from the low inlet 131 flows along the extension direction of the low upper flow path section 130. The flow velocity vector of the refrigerant flowing along the extension direction of the low upper flow path section 130 has a downward flow velocity vector component in the up-down direction DR1 and a rightward flow velocity vector component in the left-right direction DR3.

[0259] Then, when the refrigerant flowing through the low upstream flow passage section 130 flows into the downstream flow passage section 140 from the low merging port 132, it merges with the refrigerant flowing into the downstream flow passage section 140 from the rapid merging port 122, collides with it, and the flow of the refrigerant is changed by 60°. Then, the refrigerant flowing into the downstream flow passage section 140 from the rapid merging port 122 and the low merging port 132 flows along the direction in which the downstream flow passage section 140 extends, and flows out from the refrigerant outlet 143 to the compressor outlet pipe 11c. The flow velocity vector of the refrigerant flowing into the downstream flow passage section 140 from the rapid merging port 122 and the low merging port 132 has a flow velocity vector component in the downward direction of the up-down direction DR1, and has almost no flow velocity vector components in other directions. Hereinafter, the operation mode of the refrigerant cycle device 10 in which refrigerant collision occurs inside the housing 110 is also called a refrigerant collision occurrence mode.

[0260] Here, the pressure loss when the refrigerant collides in the refrigerant collision occurrence mode and the pressure loss when the refrigerant flow direction changes will be explained in comparison with the first comparative connection device 101 shown in Figure 10 and the second comparative connection device 102 shown in Figure 11.

[0261] A first comparative connection device 101 shown in FIG. 10 has a T-shape with an outer shell protruding upward in the up-down direction DR1, and has a refrigerant passage formed therein through which a refrigerant flows.

[0262] Specifically, the first comparative connection device 101 has a comparative first upstream path section 101a extending leftward from the right surface in the left-right direction DR3, and a comparative second upstream path section 101b extending rightward from the left surface in the left-right direction DR3. The left end of the comparative first upstream path section 101a in the left-right direction DR3 and the right end of the comparative second upstream path section 101b in the left-right direction DR3 are connected approximately at the center of the first comparative connection device 101 in the left-right direction DR3.

[0263] The first comparative connection device 101 also has a comparative downstream path section 101c formed by extending upward in the vertical direction DR1 from a portion where the comparative first upstream path section 101a and the comparative second upstream path section 101b are connected. The comparative downstream path section 101c is formed by penetrating from a portion where the comparative first upstream path section 101a and the comparative second upstream path section 101b are connected to an upper surface of the first comparative connection device 101 in the vertical direction DR1.

[0264] The comparative downstream path section 101c has a lower end in the up-down direction DR1 connected to the comparative first upstream path section 101a and the comparative second upstream path section 101b. The extending direction of the comparative first upstream path section 101a and the comparative second upstream path section 101b is perpendicular to the extending direction of the comparative downstream path section 101c. That is, the comparative first upstream path section 101a and the comparative second upstream path section 101b extend from the portion where they join the comparative downstream path section 101c at an angle of 90° with respect to the direction toward the downstream side of the refrigerant flow of the comparative downstream path section 101c.

[0265] The first comparison connection device 101 has an air conditioning inlet piping 11a connected to a comparison first upstream path section 101a, a cooling section inlet piping 11b connected to a comparison second upstream path section 101b, and a compressor outlet piping 11c connected to a comparison downstream path section 101c.

[0266] In the first comparative connection device 101 configured in this manner, when the refrigerant flows in from the air conditioning inlet pipe 11a, the refrigerant flowing in the comparative first upstream path section 101a flows from the right to the left in the left-right direction DR3, as shown by the refrigerant flow F10 in Fig. 10. In contrast, when the refrigerant flows in from the cooling section inlet pipe 11b, the refrigerant flowing in the comparative second upstream path section 101b flows from the left to the right in the left-right direction DR3, as shown by the refrigerant flow F11 in Fig. 10.

[0267] That is, the refrigerant flowing through the comparative first upstream path section 101a and the refrigerant flowing through the comparative second upstream path section 101b flow in opposite directions, and the refrigerant flowing through the comparative first upstream path section 101a and the comparative second upstream path section 101b collide when joining the comparative downstream path section 101c.

[0268] In addition, the refrigerant flowing through the comparative first upstream path section 101a and the comparative second upstream path section 101b has its flow direction changed by 90° when it merges with the comparative downstream path section 101c, and flows toward the upper side in the vertical direction DR1, as shown by the refrigerant flow F12 in Figure 10.

[0269] Such collisions and changes in the flow direction of the refrigerant when the refrigerants join together cause pressure losses when the refrigerant flows inside the first comparative connection device 101.

[0270] Moreover, a second comparative connection device 102 shown in FIG. 11 has an outer shell in the shape of a rectangular parallelepiped, and has a refrigerant passage formed therein through which a refrigerant flows.

[0271] Specifically, the second comparative connection device 102 has a comparative first upstream path section 102a formed from the right surface in the left-right direction DR3 toward the left side, and a comparative second upstream path section 102b formed from the rear surface in the front-rear direction DR2 toward the front side. The left end of the comparative first upstream path section 102a in the left-right direction DR3 and the front end of the comparative second upstream path section 102b in the front-rear direction DR2 are connected at approximately the center of the second comparative connection device 102 in the left-right direction DR3 and the front-rear direction DR2.

[0272] The second comparative connection device 102 also has a comparative downstream flow path section 102c formed by extending downward in the up-down direction DR1 from a portion where the comparative first upstream flow path section 102a and the comparative second upstream flow path section 102b are connected. The comparative downstream flow path section 102c is formed by penetrating from a portion where the comparative first upstream flow path section 102a and the comparative second upstream flow path section 102b are connected to the lower surface of the second comparative connection device 102 in the up-down direction DR1.

[0273] The comparative downstream flow path section 102c has an upper end in the up-down direction DR1 connected to the comparative first upstream flow path section 102a and the comparative second upstream flow path section 102b. The extension direction of the comparative first upstream flow path section 102a and the comparative second upstream flow path section 102b is perpendicular to the extension direction of the comparative downstream flow path section 102c. That is, the comparative first upstream flow path section 102a and the comparative second upstream flow path section 102b extend from the portion where they merge with the comparative downstream flow path section 102c at an angle of 90° with respect to the direction toward the downstream side of the refrigerant flow of the comparative downstream flow path section 102c.

[0274] The second comparison connection device 102 has an air conditioning inlet pipe 11a connected to a comparison first upstream flow path section 102a, a cooling section inlet pipe 11b connected to a comparison second upstream flow path section 102b, and a compressor outlet pipe 11c connected to a comparison downstream flow path section 102c.

[0275] In the second comparative connection device 102 configured in this manner, when the refrigerant flows in from the air conditioning inlet pipe 11a, the refrigerant flowing in the comparative first upstream path section 102a flows from the right to the left in the left-right direction DR3, as shown by refrigerant flow F20 in Fig. 11. In contrast, when the refrigerant flows in from the cooling section inlet pipe 11b, the refrigerant flowing in the comparative second upstream path section 102b flows from the rear side to the front side in the front-rear direction DR2, as shown by refrigerant flow F21 in Fig. 11.

[0276] The refrigerant that has flowed through the comparative first upstream path section 102a and the comparative second upstream path section 102b collides when joining the comparative downstream side path section 102c.

[0277] In addition, the refrigerant flowing through the comparative first upstream path section 102a and the comparative second upstream path section 102b has its flow direction changed by 90° when it merges with the comparative downstream path section 101c, and flows downward in the vertical direction DR1, as shown by the refrigerant flow F22 in Figure 11.

[0278] Such collisions and changes in the flow direction of the refrigerant when the refrigerants join together cause pressure losses when the refrigerant flows inside the second comparative connection device 102.

[0279] The pressure loss due to the collision of the refrigerants increases as the flow velocity vectors of the refrigerants before the collision are decomposed into the vertical direction DR1, the front-rear direction DR2, and the left-right direction DR3, and the more flow velocity vector components in the opposite directions are included.In contrast, the pressure loss decreases as the flow velocity vectors of the refrigerants before the collision are decomposed into the vertical direction DR1, the front-rear direction DR2, and the left-right direction DR3, and the more flow velocity vector components in the same direction are included.

[0280] Here, in the first comparative connection device 101 and the second comparative connection device 102, the refrigerant passage connected to the air conditioning inlet piping 11a and the cooling section inlet piping 11b is the upstream refrigerant passage, and the refrigerant passage connected to the compressor outlet piping 11c is the downstream refrigerant passage.

[0281] The pressure loss when the refrigerant flow direction changes increases as the difference between the flow direction of the refrigerant flowing through the upstream refrigerant passage and the flow direction of the refrigerant flowing through the downstream refrigerant passage increases. In other words, when the direction from the point where the upstream refrigerant passage joins with the downstream refrigerant passage toward the downstream side of the refrigerant flow in the downstream refrigerant passage is defined as a reference direction, the pressure loss increases as the extension direction of the upstream refrigerant passage deviates from the reference direction.

[0282] In the first comparative connection device 101, the refrigerants flowing through the comparative first upstream path section 101a and the comparative second upstream path section 101b flow in opposite directions and collide with each other, which tends to increase the pressure loss due to the collision when the refrigerants join. In addition, in the first comparative connection device 101, when the refrigerants flowing through the comparative first upstream path section 101a and the comparative second upstream path section 101b join the comparative downstream path section 101c, the flow directions of the refrigerants are changed by 90°. This tends to increase the pressure loss even more.

[0283] In contrast, in the second connection device for comparison 102, the refrigerant flowing through the first upstream path section 102a for comparison and the second upstream path section 102b for comparison does not include flow velocity vectors in mutually opposing directions. Therefore, pressure loss due to collision is suppressed compared to the first connection device for comparison 101.

[0284] However, in the second connection device for comparison 102, when the refrigerant flowing through the first upstream path section for comparison 102a and the second upstream path section for comparison 102b joins the downstream side path section for comparison 102c, the flow direction of each refrigerant is changed by 90°, which tends to increase the pressure loss.

[0285] In a so-called refrigerant pipe connection block that joins refrigerant flowing from multiple refrigerant pipes and guides them to a refrigerant pipe downstream of the refrigerant flow, a configuration in which the flow direction of the refrigerant changes by 90° when the refrigerants join and collide is often adopted from the viewpoint of ease of manufacture. However, such a collision and change in the flow direction of the refrigerant when the refrigerants join causes a pressure loss when the refrigerant flows inside the refrigerant pipe connection block.

[0286] In the vehicle air conditioner 1 mounted on an electric vehicle, high performance battery cooling is required from the viewpoint of extending the driving range and shortening the time for quick charging, and therefore a method for suppressing pressure loss in the refrigeration cycle device 10 is an issue. In order to suppress the pressure loss, there is a method of increasing the inner diameter of the refrigerant pipes connecting the various components of the refrigeration cycle device 10 to reduce the pressure loss when the refrigerant flows. However, this method is not preferable because it increases the cost of the refrigerant pipes, which causes an increase in the manufacturing cost of the refrigeration cycle device 10 as a whole. For this reason, a refrigerant pipe connection block that can suppress the pressure loss without increasing the inner diameter of the refrigerant pipes is required.

[0287] In contrast, in the connection device 100 of this embodiment, the steep upward flow path section 120 extends from the first junction 141 at an angle of 30° relative to the predetermined junction reference direction DRC. Also, in the connection device 100, the low upward flow path section 130 extends from the second junction 142 at an angle of 60° relative to the predetermined junction reference direction DRC. Furthermore, in the connection device 100, the first junction 141 is provided at a position upstream of the second junction 142 in the refrigerant flow direction.

[0288] In the connection device 100 thus formed, the refrigerant does not flow into the downstream flow passage section 140 at the downstream flow passage section 140 upstream of the first junction 141 in the refrigerant flow direction. Therefore, at the first junction 141, when the refrigerant flowing through the steep upward flow passage section 120 flows into the downstream flow passage section 140, the refrigerant that has flowed into the downstream flow passage section 140 does not collide with the refrigerant that has flowed into the downstream flow passage section 140 from a flow passage section other than the steep upward flow passage section 120.

[0289] Therefore, when the refrigerant flowing through the steep upward flow passage section 120 flows into the downstream side flow passage section 140, no pressure loss due to collision occurs.

[0290] In addition, when the refrigerant flowing through the low upstream flow path section 130 flows into the downstream flow path section 140, the refrigerant flowing into the downstream flow path section 140 merges with the refrigerant flowing into the downstream flow path section 140 from the steep upstream flow path section 120 at the second junction section 142 and collides.

[0291] The flow velocity vector of the refrigerant flowing through the low upstream flow path section 130 immediately before it flows into the second junction 142 has a downward flow velocity vector component in the up-down direction DR1 and a rightward flow velocity vector component in the left-right direction DR3. In contrast, the flow velocity vector of the refrigerant that has flowed from the steep upstream flow path section 120 into the downstream side flow path section 140 immediately before it flows into the second junction 142 has a downward flow velocity vector component in the up-down direction DR1 and has almost no flow velocity vector components in other directions.

[0292] In this way, the flow velocity vector of the refrigerant flowing from the lower upstream flow path section 130 to the second junction 142 does not include a flow velocity vector in a direction opposite to the flow velocity vector of the refrigerant flowing upstream of the second junction 142 in the downstream side flow path section 140. Therefore, pressure loss due to collisions when the refrigerants merge is suppressed compared to the first comparative connection device 101.

[0293] In addition, the refrigerant flowing from the steep upward flow path section 120 to the downstream side flow path section 140 has its flow direction changed by the first angle θ1 and flows downward in the up-down direction DR1. Specifically, the refrigerant flowing from the steep upward flow path section 120 to the downstream side flow path section 140 has its flow direction changed by 30°.

[0294] That is, the amount of change in the flow direction of the refrigerant when it flows from the steep upward flow path section 120 to the downstream side flow path section 140 is 30°. This amount of change is smaller than the amount of change in the flow direction of the refrigerant, which is 90°, when it flows from the upstream side refrigerant passage in the first comparative connection device 101 and the second comparative connection device 102 to join the downstream side refrigerant passage.

[0295] The refrigerant flowing from the low upstream flow path section 130 into the downstream side flow path section 140 has its flow direction changed by the second angle θ2, merges with the refrigerant flowing from the steep upstream flow path section 120, and flows downward in the vertical direction DR1. Specifically, the refrigerant flowing from the low upstream flow path section 130 into the downstream side flow path section 140 has its flow direction changed by 60°.

[0296] That is, the amount of change in the flow direction of the refrigerant when it flows from the lower upstream flow path section 130 to the downstream side flow path section 140 is 60°. This amount of change is smaller than the amount of change in the flow direction of the refrigerant, which is 90°, when it flows from the upstream side refrigerant passage in the first comparative connection device 101 and the second comparative connection device 102 to the downstream side refrigerant passage.

[0297] Therefore, the pressure loss when the refrigerant flow direction changes in this embodiment is suppressed compared to the pressure loss when the refrigerant flow direction changes in the first comparative connection device 101 and the second comparative connection device 102.

[0298] As described above, in the connection device 100 of this embodiment, the steep upward flow path section 120 extends at a first angle θ1 of 30° with respect to the predetermined merging reference direction DRC. The low upper flow path section 130 extends at a second angle θ2 of 60° with respect to the predetermined merging reference direction DRC. This makes it possible to suppress pressure loss when the refrigerant changes its flow direction when merging from the steep upward flow path section 120 and the low upper flow path section 130 into the downstream side flow path section 140.

[0299] (1) In the above embodiment, both the steep upward flow passage section 120 and the low upper flow passage section 130 extend at an angle greater than 0° and less than 90° with respect to the predetermined merging reference direction DRC. This makes it possible to reduce pressure loss more than in a configuration in which one of the steep upward flow passage section 120 and the low upper flow passage section 130 extends at an angle greater than 0° and less than 90° with respect to the predetermined merging reference direction DRC and the other extends at an angle greater than 90° with respect to the predetermined merging reference direction DRC.

[0300] (2) In the above embodiment, the inner diameter of the downstream flow passage section 140 downstream of the first junction section 141 in the refrigerant flow direction is larger than the inner diameter of the steep upward flow passage section 120, and the inner diameter of the downstream of the second junction section 142 in the refrigerant flow direction is larger than the inner diameter of the low upward flow passage section 130.

[0301] Therefore, the speed of the refrigerant flowing through the downstream flow passage section 140 is slower than when the refrigerant flow downstream side of the first junction section 141 is equal to or smaller than the inner diameter of the steep upward flow passage section 120, and the refrigerant flow downstream side of the second junction section 142 is equal to or smaller than the inner diameter of the low upstream flow passage section 130. Therefore, pressure loss occurring when the refrigerant flows through the downstream flow passage section 140 can be suppressed compared to when the inner diameter of the downstream flow passage section 140 is equal to or smaller than the inner diameters of the steep upward flow passage section 120 and the low upstream flow passage section 130.

[0302] (3) In the above embodiment, in the connection device 100, the air conditioning inlet pipe 11a is connected to the steep upward flow path section 120, the cooling section inlet pipe 11b is connected to the low upward flow path section 130, and the compressor outlet pipe 11c is connected to the downstream side flow path section 140. Also, the direction in which the steep upward flow path section 120 extends with respect to the predetermined merging reference direction DRC is smaller than the direction in which the low upward flow path section 130 extends with respect to the predetermined merging reference direction DRC. That is, the first angle θ1 is smaller than the second angle θ2.

[0303] Here, the vehicle air conditioner 1 mounted on the electric vehicle places more importance on air conditioning the vehicle cabin than on cooling the battery 60. For this reason, in the refrigeration cycle device 10 operating in the refrigerant collision occurrence mode, it is necessary to flow more refrigerant into the air conditioning inlet pipe 11a than into the cooling section inlet pipe 11b. In this case, more refrigerant flows into the connection device 100 from the steep upward flow path section 120 than from the low upward flow path section 130.

[0304] For this reason, the pressure loss that occurs when merging into the downstream flow path section 140 from the steep upstream flow path section 120 has a greater impact on the pressure loss of the entire refrigeration cycle apparatus 10 than the pressure loss that occurs when merging from the low upstream flow path section 130.

[0305] In the above embodiment, the first angle θ1 is smaller than the second angle θ2. Therefore, the amount of change in the flow direction of the refrigerant when merging into the downstream flow passage section 140 is smaller when merging from the steep upward flow passage section 120 to the downstream flow passage section 140 than when merging from the low upward flow passage section 130 to the downstream flow passage section 140. Therefore, the pressure loss when the flow direction of the refrigerant changes when merging from the steep upward flow passage section 120 to the downstream flow passage section 140 can be suppressed more than the pressure loss when the flow direction of the refrigerant changes when merging from the low upward flow passage section 130 to the downstream flow passage section 140.

[0306] Therefore, when more refrigerant flows through the air conditioning inlet pipe 11a than through the cooling unit inlet pipe 11b, the pressure loss in the entire refrigeration cycle apparatus 10 can be suppressed compared to a case not configured in this manner.

[0307] (4) In the above embodiment, the most downstream side of the refrigerant flow of the downstream passage section 140 is provided at a position vertically lower than the most upstream side of the refrigerant flow of the steep upward passage section 120 and the most upstream side of the refrigerant flow of the low upward passage section 130. In other words, the refrigerant outlet 143 is positioned vertically lower than the steep upward inlet 121 and the low upward inlet 131.

[0308] As described above, when the second expansion valve 17b in the dehumidifying heating mode of the vehicle air conditioner 1 operates in the throttling state and in the cooling mode, the refrigerant flows into the connection device 100 from the rapid flow inlet 121 but does not flow into the connection device 100 from the low flow inlet 131. Also, when the vehicle air conditioner 1 operates in the heating mode and the cooling mode, the refrigerant flows into the connection device 100 from the low flow inlet 131 but does not flow into the connection device 100 from the rapid flow inlet 121.

[0309] In this way, when the refrigerant flows in through only one of the inlets, either the rapid flow inlet 121 or the low flow inlet 131, there is a risk that the oil that flows into the inside of the housing 110 together with the refrigerant will flow back inside the housing 110 and flow out to the outside through the other inlet through which the refrigerant does not flow.

[0310] In the above embodiment, refrigerant outlet 143 is positioned vertically lower than rapid inlet 121 and slow inlet 131, so that oil that flows into housing 110 together with the refrigerant easily flows vertically downward. Therefore, even in an operation mode in which refrigerant flows in only from one inlet, it is possible to prevent the oil that has flowed in from flowing back inside housing 110 and flowing out from the inlet on the side to which the refrigerant does not flow in.

[0311] Furthermore, the refrigerant outlet 143 is formed in the bottom surface portion 111 of the connection device 100 so that the opening direction faces vertically downward. When the connection device 100 is provided inside the vehicle air conditioner 1, the refrigerant outlet 143 is provided at a position vertically above the refrigerant suction port 12a of the compressor 12.

[0312] Therefore, when the vehicle air conditioner 1 stops operating, the oil that flows out together with the refrigerant from the refrigerant outlet 143 can be prevented from flowing back inside the housing 110 and flowing out from the rapid flow inlet 121 and the low flow inlet 131.

[0313] (5) In the above embodiment, the inner diameter of the steep upward flow passage section 120 is formed to a size corresponding to the most downstream portion of the refrigerant flow in the air conditioning inlet pipe 11a, and the inner diameter of the low upward flow passage section 130 is formed to a size corresponding to the most downstream portion of the refrigerant flow in the cooling section inlet pipe 11b. Also, the inner diameter of the downstream side flow passage section 140 is larger than the inner diameters of the steep upward flow passage section 120 and the low upward flow passage section 130, and is formed to a size corresponding to the most upstream portion of the refrigerant flow in the compressor outlet pipe 11c.

[0314] Therefore, it is not necessary to take measures such as attaching a refrigerant piping conversion member for connecting air conditioning inlet piping 11a to rapid flow inlet 121 or attaching a refrigerant piping conversion member for connecting cooling unit inlet piping 11b to low flow inlet 131. In addition, it is not necessary to take measures such as attaching a refrigerant piping conversion member for connecting compressor outlet piping 11c to refrigerant outlet 143.

[0315] Therefore, it is possible to suppress the pressure loss that occurs when the refrigerant flows through the downstream channel portion 140, and also to suppress an increase in manufacturing costs.

[0316] (6) In the above embodiment, the first junction 141 and the second junction 142 are provided at different positions in the downstream flow passage section 140. Specifically, the first junction 141 is positioned upstream of the refrigerant flow than the second junction 142. Therefore, when the steep upward flow passage section 120 and the low upward flow passage section 130 join in the downstream flow passage section 140, the position where the steep upward flow passage section 120 joins and the position where the low upward flow passage section 130 joins can be located at different positions.

[0317] Therefore, when the refrigerant merging from the steep upstream flow path section 120 connected to the first merging section 141 merges into the downstream flow path section 140, it is possible to avoid collision with the refrigerant merging from the low upstream flow path section 130 into the downstream flow path section 140. Therefore, compared to a case not configured in this way, it is possible to suppress pressure loss due to collision when the refrigerant merges in the downstream flow path section 140.

[0318] (7) In the above embodiment, in the downstream channel section 140, the first junction section 141 is provided at a position further upstream in the refrigerant flow direction than the second junction section 142.

[0319] Incidentally, in the downstream-side flow path section 140, when a refrigerant passage merges with the downstream-side flow path section 140 at a midway point of the flow path, the refrigerant flowing through the downstream-side flow path section 140 generates a force that draws the refrigerant flowing through the merging refrigerant passage into the downstream-side flow path section 140. The force that draws the refrigerant into the downstream-side flow path section 140 becomes larger as the flow rate of the refrigerant flowing through the downstream-side flow path section 140 increases.

[0320] Furthermore, as described above, in the refrigerant collision occurrence mode of the vehicle air conditioning system 1, which is more often used to condition the interior of the vehicle cabin than to cool the battery 60, more refrigerant flows into the connection device 100 from the steep upward flow path section 120 than from the low upward flow path section 130.

[0321] In the above embodiment, the first junction 141 is provided at a position upstream of the second junction 142 in the refrigerant flow direction, so that the refrigerant flowing through the low upstream flow path section 130 merges with the downstream flow path section 140 through which the refrigerant flowing in from the steep upstream flow path section 120 flows. Therefore, the flow of the refrigerant flowing in from the steep upstream flow path section 120, through which more refrigerant flows than the low upstream flow path section 130, can generate a force that draws the refrigerant flowing through the low upstream flow path section 130, which merges with the refrigerant in the middle of the refrigerant passage, into the downstream flow path section 140.

[0322] Therefore, compared to a configuration in which the first junction 141 is located downstream of the second junction 142 in the refrigerant flow direction, the force drawing the refrigerant into the downstream flow path section 140 can be made greater, thereby suppressing pressure loss when the refrigerant flow direction changes. (First modified example of the first embodiment) In the above-described first embodiment, an example has been described in which the steep upward flow passage section 120 and the low upward flow passage section 130 are formed so that the first angle θ1 is smaller than the second angle θ2, but the present invention is not limited to this. For example, the steep upward flow passage section 120 and the low upward flow passage section 130 may be configured so that the first angle θ1 is larger than the second angle θ2 as long as the angle is greater than 0° and smaller than 90°. Furthermore, the steep upward flow passage section 120 and the low upward flow passage section 130 may be configured so that the first angle θ1 and the second angle θ2 are the same angle as long as the angle is greater than 0° and smaller than 90°. (Second Modification of the First Embodiment) In the above-described first embodiment, an example has been described in which the first junction 141 is provided upstream of the second junction 142 in the refrigerant flow in the downstream passage section 140, but the present invention is not limited thereto. For example, the first junction 141 may be provided at a position downstream of the second junction 142 in the refrigerant flow in the downstream passage section 140. In addition, the steep upward passage section 120 and the low upward passage section 130 may be configured to join the downstream passage section 140 at positions equal to each other.

[0323] Second embodiment Next, a second embodiment will be described with reference to Figures 12 to 14. In this embodiment, the outer diameter of the air conditioning inlet pipe 11a, the shape of the housing 210, and the shape of the refrigerant passage formed inside the housing 210 are different from those of the first embodiment. In this embodiment, the parts different from the first embodiment will be mainly described, and the description of the parts similar to the first embodiment may be omitted.

[0324] The air conditioning inlet pipe 11a of this embodiment is a refrigerant pipe having an outer diameter of 19.05 mm from the inlet side to the outlet side. The outer diameter of the air conditioning inlet pipe 11a is larger than the outer diameter of the cooling section inlet pipe 11b and is the same as the outer diameter of the compressor outlet pipe 11c. That is, the air conditioning inlet pipe 11a of this embodiment is a refrigerant pipe having an outer diameter larger than that of the air conditioning inlet pipe 11a of the first embodiment.

[0325] As shown in Figures 12 and 13, the connection device 200 has a housing 210, and inside the housing 210, a series upstream path section 220, an inclined upstream path section 230, and a series downstream path section 250, which are refrigerant paths, are formed.

[0326] The housing 210 of this embodiment is formed in a cubic shape in which the size in the up-down direction DR1 is larger than the size in the front-rear direction DR2 and the size in the left-right direction DR3. The housing 210 has an upper surface portion 211 provided on the upper side in the up-down direction DR1 and a lower surface portion 212 provided on the lower side in the up-down direction DR1. The housing 210 also has a right surface portion 213 that extends from the right end of the upper surface portion 211 in the left-right direction DR3 toward the lower side in the up-down direction DR1 to the right end of the lower surface portion 212 in the left-right direction DR3. The housing 210 also has a left surface portion 214 that extends from the left end of the upper surface portion 211 in the left-right direction DR3 toward the lower side in the up-down direction DR1 to the left end of the lower surface portion 212 in the left-right direction DR3.

[0327] 12, inside the housing 210, a serial upstream path section 220 is formed as a refrigerant path, extending from the surface of the upper surface section 211 toward the lower surface section 212. Also, inside the housing 210, an inclined upstream path section 230 is formed, extending at an angle from the surface of the right surface section 213 toward the left surface section 214 without penetrating all the way to the left surface section 214. Also, inside the housing 210, a serial downstream path section 250 is formed, extending from the surface of the lower surface section 212 toward the upper side in the up-down direction DR1.

[0328] The serial upstream path section 220 extends linearly in the up-down direction DR1 from approximately the center of the surface of the upper surface section 211 toward approximately the center of the lower surface section 212. Furthermore, of both ends of the serial upstream path section 220, ends opposite to the side positioned on the surface of the upper surface section 211 are connected to ends opposite to the side positioned on the surface of the lower surface section 212 of both ends of the serial downstream path section 250. Furthermore, of both ends of the serial upstream path section 220, ends opposite to the side positioned on the surface of the upper surface section 211 are connected to ends opposite to the side positioned on the surface of the right surface section 213 of both ends of the inclined upstream path section 230.

[0329] The inclined upper flow path section 230 extends from a portion of the surface of the right face section 213 that is above the center in the up-down direction DR1 toward a portion of the left face section 214 that is below the center in the up-down direction DR1. Furthermore, of both ends of the inclined upper flow path section 230, ends opposite the side positioned on the surface of the right face section 213 are connected to ends opposite the side positioned on the surface of the lower face section 212 of both ends of the serial downstream flow path section 250. Furthermore, of both ends of the inclined upper flow path section 230, ends opposite the side positioned on the surface of the right face section 213 are connected to ends opposite the side positioned on the surface of the upper face section 211 of both ends of the serial upstream flow path section 220.

[0330] That is, in this embodiment, the series upstream path section 220, the inclined upper path section 230, and the series downstream path section 250 are directly connected. Specifically, the most downstream refrigerant flow portion of the series upstream path section 220 and the most downstream refrigerant flow portion of the inclined upper path section 230 are directly connected at the most upstream refrigerant flow portion of the series downstream path section 250. Therefore, the refrigerant flowing from the series upstream path section 220 to the series downstream path section 250 and the refrigerant flowing from the inclined upper path section 230 to the series downstream path section 250 directly merge into the series downstream path section 250. In this embodiment, the series upstream path section 220 functions as a series upstream path section, the inclined upper path section 230 functions as a inclined upstream path section, and the series downstream path section 250 functions as a downstream path section.

[0331] The series upstream path section 220 forms a refrigerant passage for guiding the refrigerant flowing out from the air conditioning inlet pipe 11a into the housing 210, and extends linearly in the same direction as the extension direction of the series downstream path section 250. The series upstream path section 220 has a series inlet 221 to which the air conditioning inlet pipe 11a is connected on the upstream side of the refrigerant flow, and a series junction port 222 communicating with the series downstream path section 250 on the downstream side of the refrigerant flow. For ease of explanation, the series junction port 222 is indicated by a dashed line in Fig. 13. The extension direction of the series upstream path section 220 will be described later.

[0332] The serial upstream path section 220 is formed such that a fourth inner diameter φ4, which is the inner diameter of the serial upstream path section 220, is slightly larger than the outer diameter of the air conditioning inlet pipe 11a, and is formed so that the air conditioning inlet pipe 11a can be inserted into the serial upstream path section 220 from the serial inlet 221. Specifically, the inner diameter of the serial upstream path section 220 is formed slightly larger than the outer diameter 19.05 mm of the air conditioning inlet pipe 11a.

[0333] The serial upstream path section 220 is formed so that the fourth inner diameter φ4 is uniform from the serial inlet 221 to the serial junction port 222. The fourth inner diameter φ4 is the diameter of a cross-sectional shape in a direction perpendicular to the extension direction of the serial upstream path section 220. The inner diameter of the serial upstream path section 220 is larger than the inner diameter of the inclined upstream path section 230 and is formed to be the same size as the inner diameter of the serial downstream path section 250.

[0334] The inclined upstream flow path section 230 forms a refrigerant passage for guiding the refrigerant flowing out from the cooling unit inlet pipe 11b into the housing 210. The inclined upstream flow path section 230 extends linearly in a direction different from the direction in which the series upstream flow path section 220 and the direction in which the series downstream flow path section 250 extend.

[0335] The inclined upstream passage section 230 has an inclined inlet 231 to which the cooling section inlet pipe 11b is connected on the upstream side of the refrigerant flow, and has an inclined junction port 232 on the downstream side of the refrigerant flow that communicates with the serial downstream passage section 250. The direction in which the inclined upstream passage section 230 extends will be described later.

[0336] The inclined upstream passage section 230 is formed such that a fifth inner diameter φ5 which is the inner diameter of the inclined upstream passage section 230 is slightly larger than the outer diameter of the cooling section inlet pipe 11b, and is formed so that the cooling section inlet pipe 11b can be inserted into the inclined upstream passage section 230 from the inclined inlet 231. Specifically, the inner diameter of the inclined upstream passage section 230 is formed slightly larger than the outer diameter 15.88 mm of the cooling section inlet pipe 11b.

[0337] The inclined upper passage section 230 is formed so that the fifth inner diameter φ5 is uniform from the upstream side of the refrigerant flow to the downstream side of the refrigerant flow. The fifth inner diameter φ5 is the diameter of a cross-sectional shape in a direction perpendicular to the extension direction of the inclined upper passage section 230.

[0338] The serial downstream path section 250 forms a refrigerant passage for allowing the refrigerant, which has flowed into the inside of the housing 210 via the serial upstream path section 220 and the inclined upstream path section 230, to flow out of the housing 210. The serial downstream path section 250 extends linearly from approximately the center of the surface of the lower face section 212 toward approximately the center of the upper face section 211 along the up-down direction DR1.

[0339] The position where the serial downstream path section 250 is formed coincides with the position where the serial upstream path section 220 is formed in the front-rear direction DR2 and the left-right direction DR3. That is, the serial downstream path section 250 is formed on the same straight line as the serial upstream path section 220.

[0340] The series downstream path section 250 has a multiple junction section 251 on the upstream side of the refrigerant flow that merges the refrigerant flowing through the series upstream path section 220 and the inclined upstream path section 230 into the series downstream path section 250. In addition, the series downstream path section 250 has a series outlet port 253 on the most downstream side of the refrigerant flow to which the compressor outflow pipe 11c is connected.

[0341] Here, the portion where a straight line L4 that passes through the center of the serial outlet 253 and along the extension direction of the serial downstream path section 250 intersects with a straight line L5 that passes through the center of the serial inlet 221 and along the extension direction of the serial upstream path section 220 is defined as a multiple junction section 251. The multiple junction section 251 is also the portion where a straight line L4 that passes through the center of the serial outlet 253 and along the extension direction of the serial downstream path section 250 intersects with a straight line L6 that passes through the center of the inclined inlet 231 and along the extension direction of the inclined upstream path section 230.

[0342] That is, in the present embodiment, the position where the series upstream path section 220 joins and the position where the inclined upstream path section 230 joins are provided at the same position in the series downstream path section 250. The multiple junction section 251 is a section where the refrigerant flowing through each of the series upstream path section 220 and the inclined upstream path section 230 flows in. In the present embodiment, the multiple junction section 251 functions as a junction section.

[0343] In addition, the series downstream path section 250 has a series outlet 253 on the most downstream side of the refrigerant flow, which is provided lower in the up-down direction DR1 than the series inlet 221 on the most upstream side of the refrigerant flow of the series upstream path section 220. In addition, the series downstream path section 250 has a series outlet 253 on the most downstream side of the refrigerant flow, which is provided lower in the up-down direction DR1 than the inclined inlet 231 on the most upstream side of the refrigerant flow of the inclined upstream path section 230. In other words, the series outlet 253 is positioned vertically lower than the series inlet 221 and the inclined inlet 231.

[0344] The serial downstream passage section 250 has a sixth inner diameter φ6 which is an inner diameter of the serial downstream passage section 250 and is formed slightly larger than the outer diameter of the compressor outlet pipe 11c so that the compressor outlet pipe 11c can be inserted into the serial downstream passage section 250 from the serial outlet port 253. Specifically, the inner diameter of the serial downstream passage section 250 is formed slightly larger than the outer diameter 19.05 mm of the compressor outlet pipe 11c.

[0345] The serial downstream path section 250 has a sixth inner diameter φ6 that is equal from the multiple junction 251 to the serial outlet 253. Furthermore, the sixth inner diameter φ6 is equal to the fourth inner diameter φ4. In contrast, the sixth inner diameter φ6 is larger than the fifth inner diameter φ5. That is, the inner diameter of the serial downstream path section 250 downstream of the multiple junction 251 in the refrigerant flow direction is equal to the inner diameter of the serial upstream path section 220 and larger than the inner diameter of the inclined upstream path section 230.

[0346] In other words, the cross-sectional area of ​​the series downstream path section 250, at the refrigerant flow downstream side of the multiple junction 251, perpendicular to the refrigerant flow direction is equal to the cross-sectional area of ​​the series upstream path section 220. Moreover, the cross-sectional area of ​​the series downstream path section 250, at the refrigerant flow downstream side of the multiple junction 251, perpendicular to the refrigerant flow direction is larger than the cross-sectional area of ​​the inclined upstream path section 230 perpendicular to the refrigerant flow direction.

[0347] In this embodiment, the ratio of the inner diameter of the series downstream passage section 250 to the inner diameter of the series upstream passage section 220 is 1. In contrast, the ratio of the inner diameter of the series downstream passage section 250 to the inner diameter of the inclined upper passage section 230 is 1.20.

[0348] Next, the details of the direction in which the series upstream passage section 220 and the inclined upstream passage section 230 extend will be described using a predetermined merging reference direction DRC. Here, a direction along the up-down direction DR1 that extends from the multiple merging section 251 toward the downstream side of the refrigerant flow of the series downstream passage section 250 is defined as a downstream direction, and a direction opposite to the downstream direction is defined as a predetermined merging reference direction DRC. The predetermined merging reference direction DRC is a direction toward the upper side along the up-down direction DR1 with the multiple merging section 251 as a reference.

[0349] As described above, the serial upstream path section 220 extends linearly in the same direction as the serial downstream path section 250. Therefore, the serial upstream path section 220 extends along a predetermined junction reference direction DRC. Therefore, the angle formed by the predetermined junction reference direction DRC and the direction in which the serial upstream path section 220 extends, with the multiple junction section 251 as the center, is 0°. The direction in which the serial upstream path section 220 extends does not include the left-right direction DR3 and the front-rear direction DR2.

[0350] In contrast, the inclined upper flow passage section 230 extends at a third angle θ3 greater than 0° and smaller than 90° with respect to the predetermined junction reference direction DRC with respect to the multiple junction section 251 as a reference. Here, the angle extending from the multiple junction section 251 with respect to the predetermined junction reference direction DRC is an angle in which the upper side of the vertical direction DR1 is set as 0° and the clockwise direction is set as the positive direction in the cross-sectional view shown in Fig. 13. The third angle θ3 is an angle formed by the predetermined junction reference direction DRC and the direction in which the inclined upper flow passage section 230 extends with the multiple junction section 251 as the center.

[0351] In this embodiment, the inclined upper flow path section 230 extends so that the third angle θ3 is 45°. Thus, the direction in which the inclined upper flow path section 230 of this embodiment extends includes the left-right direction DR3 and the up-down direction DR1, but does not include the front-rear direction DR2. Note that the third angle θ3 may be an angle greater than 45° or less than 45° as long as it is within a range greater than 0° and less than 90°.

[0352] Next, the flow of the refrigerant and the pressure loss when the refrigerant flows inside the connection device 200 of this embodiment when the refrigeration cycle apparatus 10 is operated in the refrigerant collision generation mode will be described with reference to FIG. 14. In this embodiment, the refrigerant flowing through the series upstream path section 220 flows downward in the vertical direction DR1 along the direction in which the series upstream path section 220 extends, as shown by the refrigerant flow F5 in FIG. 14. The flow velocity vector of the refrigerant flowing along the direction in which the series upstream path section 220 extends has a flow velocity vector component in the downward direction of the vertical direction DR1, and has no flow velocity vector components in other directions. That is, the flow velocity vector of the refrigerant when flowing from the series junction port 222 into the series downstream path section 250 has a flow velocity vector component in the downward direction of the vertical direction DR1, and has almost no flow velocity vector components in other directions.

[0353] Moreover, the series upstream path section 220 is provided on the same straight line as the series downstream path section 250, and is formed to extend along the up-down direction DR1 which is the extension direction of the series downstream path section 250. For this reason, in this embodiment, the flow direction of the refrigerant flowing from the series junction port 222 into the series downstream path section 250 is not substantially changed when the refrigerant flows into the series downstream path section 250.

[0354] 14, the refrigerant flowing through the inclined upper flow path section 230 flows along the direction in which the inclined upper flow path section 230 extends. The flow velocity vector of the refrigerant flowing along the direction in which the inclined upper flow path section 230 extends has a downward flow velocity vector component in the up-down direction DR1 and a leftward flow velocity vector component in the left-right direction DR3, but does not have a flow velocity vector component in the front-rear direction DR2. That is, the flow velocity vector of the refrigerant when flowing from the inclined junction port 232 into the serial downstream flow path section 250 has a downward flow velocity vector component in the up-down direction DR1 and a leftward flow velocity vector component in the left-right direction DR3, but does not have a flow velocity vector in the front-rear direction DR2.

[0355] In addition, in the series downstream path section 250, the position where the series upstream path section 220 joins and the position where the inclined upstream path section 230 joins are provided at the same position. Therefore, in the connection device 200 of the present embodiment, when the refrigerant flowing through the series upstream path section 220 flows from the series junction port 222 into the series downstream path section 250, the refrigerant collides with the refrigerant flowing from the inclined upstream path section 230 into the series downstream path section 250.

[0356] The refrigerant flowing from the inclined junction port 232 into the serial downstream path section 250 merges with and collides with the refrigerant flowing from the serial junction port 222 into the serial downstream path section 250, and the flow direction of the refrigerant is changed by a third angle θ3 that is greater than 0° and less than 90°. In this embodiment, the flow direction of the refrigerant flowing from the inclined junction port 232 into the serial downstream path section 250 is changed by 45°.

[0357] As described above, in the connection device 200 of this embodiment, the shape of the housing 210 and the shape of the refrigerant passage formed inside the housing 210 are different from those of the first embodiment. The rest of the configuration and operation of the connection device 200 are the same as those of the first embodiment. As a result, it is possible to obtain the same effects as those of the first embodiment.

[0358] The series upstream path section 220 is disposed on the same straight line as the series downstream path section 250, and extends along the up-down direction DR1, which is the direction in which the series downstream path section 250 extends. For this reason, the refrigerant that has flowed into the series downstream path section 250 from the series junction port 222 flows downward in the up-down direction DR1 without changing the flow direction of the refrigerant.

[0359] Therefore, in the connection device 200 of this embodiment, pressure loss when the refrigerant flow direction changes can be suppressed compared to a configuration in which the series upstream path portion 220 extends deviated from the predetermined merging reference direction DRC.

[0360] The refrigerant flowing into the series downstream path section 250 from the inclined junction port 232 joins and collides with the refrigerant flowing into the series downstream path section 250 from the series junction port 222, and the flow direction of the refrigerant is changed by 45°. The refrigerant flowing into the series downstream path section 250 from the inclined junction port 232 flows downward in the up-down direction DR1 together with the refrigerant flowing in from the series junction port 222.

[0361] Therefore, in the connection device 200 of this embodiment, the amount of change in the flow direction of the refrigerant can be made smaller compared to when the inclined upper flow path section 230 extends at an angle of 90° relative to the predetermined merging reference direction DRC, thereby suppressing pressure loss when the flow direction of the refrigerant changes.

[0362] In addition, in the connection device 200 of this embodiment, the flow velocity vector of the refrigerant flowing from the serial upstream path section 220 into the multiple junction section 251 does not include a flow velocity vector in a direction opposite to the flow velocity vector of the refrigerant flowing from the inclined upstream path section 230 into the multiple junction section 251. Therefore, compared to a case without such a configuration, it is possible to suppress pressure loss due to collisions when the refrigerants merge.

[0363] (1) In the above embodiment, the inner diameter of the series downstream passage section 250 downstream of the multiple junction section 251 in the refrigerant flow direction is larger than the inner diameter of the inclined upstream passage section 230 .

[0364] For this reason, in the series downstream flow path section 250, the speed of the refrigerant flowing downstream of the multiple junction section 251 is slower than when the inner diameter of the refrigerant flow downstream of the multiple junction section 251 is equal to the inner diameter of the inclined upper flow path section 230. Therefore, compared to when the inner diameter of the series downstream flow path section 250 is formed to be equal to or smaller than the inner diameter of the inclined upper flow path section 230, pressure loss generated when the refrigerant flows through the series downstream flow path section 250 can be suppressed.

[0365] (2) In the above embodiment, the connection device 200 has an air conditioning inlet pipe 11a connected to the series upstream flow path section 220, a cooling section inlet pipe 11b connected to the inclined upstream flow path section 230, and a compressor outlet pipe 11c connected to the series downstream flow path section 250.

[0366] Here, as described above, when the vehicle air conditioner 1, which is more often used to condition the interior of the vehicle cabin than to cool the battery 60, is operated in the refrigerant collision generation mode, more refrigerant flows into the serial upper flow path section 220 than into the inclined upper flow path section 230 of the connection device 200.

[0367] In the above embodiment, the air conditioning inlet pipe 11a is connected to the series upstream path section 220, in which the flow direction of the refrigerant does not change substantially when merging with the series downstream path section 250. Therefore, compared to a configuration in which the air conditioning inlet pipe 11a is connected to the inclined upstream path section 230, it is possible to suppress pressure loss caused when the flow direction of the refrigerant changes when merging from the series upstream path section 220 and the inclined upstream path section 230 to the series downstream path section 250.

[0368] Therefore, when more refrigerant flows through the air conditioning inlet pipe 11a than through the cooling section inlet pipe 11b, the pressure loss throughout the refrigeration cycle apparatus 10 can be reduced compared to a case in which this configuration is not used.

[0369] Third embodiment Next, a third embodiment will be described with reference to Figs. 15 to 18. In this embodiment, as shown in Fig. 15, a rear seat air conditioning unit 80 is added to the refrigeration cycle device 10 compared to the second embodiment. In this embodiment, in conjunction with the addition of the rear seat air conditioning unit 80, a refrigerant passage through which the refrigerant flowing out from the rear seat air conditioning unit 80 flows is added inside the housing 210. In this embodiment, the differences from the second embodiment will be mainly described, and descriptions of the same parts as in the second embodiment may be omitted.

[0370] First, the rear seat air conditioning unit 80 will be described. The rear seat air conditioning unit 80 is for blowing out the blown air whose temperature has been adjusted by the refrigeration cycle device 10 into the space in the vehicle interior where the rear seats are mainly installed. In contrast, the interior air conditioning unit 50 blows out the blown air whose temperature has been adjusted by the refrigeration cycle device 10 into the space in the vehicle interior where the driver's seat is mainly installed. The first target space in this embodiment is the space in which the driver's seat is installed. Also, the second target space in this embodiment is a space different from the space in which the driver's seat is installed. Specifically, the second target space is the space in which the rear seats are installed.

[0371] 15, the rear seat air conditioning unit 80 has a rear seat evaporator 14b and a rear seat heater core 88 disposed in an air passage formed in a rear seat air conditioning case 81 that forms the outer shell of the rear seat air conditioning unit 80. Also, the interior air conditioning unit 50 has a front seat evaporator 14a disposed in the air conditioning case 51 instead of the interior evaporator 14.

[0372] The front seat evaporator 14a and the rear seat evaporator 14b correspond to the interior evaporator 14 and are cooling heat exchangers that cool the air to be blown into the vehicle cabin. The rear seat heater core 88 corresponds to the heater core 35 and is a heating heat exchanger that heats the air to be blown into the vehicle cabin. In this embodiment, the front seat evaporator 14a functions as a first air conditioning heat exchanger, and the rear seat evaporator 14b functions as a second air conditioning heat exchanger.

[0373] The rear seat air conditioning case 81 houses a rear seat inside / outside air switching device 82, a rear seat blower 83, a rear seat evaporator temperature sensor 84, and a rear seat air mix door 86. Inside the rear seat air conditioning case 81, a rear seat cool air bypass passage 85 is provided, which allows the blown air after passing through the rear seat evaporator 14b to bypass a rear seat heater core 88. Furthermore, inside the rear seat air conditioning case 81, a rear seat mixing space 87 is arranged downstream of the blown air flow of the rear seat cool air bypass passage 85.

[0374] An opening for blowing air into the space in which the rear seats are provided is disposed on the downstream side of the blown air flow of the rear seat air-conditioning case 81. This opening is an outlet for blowing air toward the passengers in the rear seats and is connected to a rear seat outlet (not shown) provided on the ceiling of the vehicle interior.

[0375] The temperature of the blown air blown out from the rear seat air outlet is adjusted by adjusting the ratio of the air volume passing through the rear seat heater core 88 and the air volume passing through the rear seat cool air bypass passage 85 by the rear seat air mix door 86.

[0376] The rear seat inside / outside air switching device 82, rear seat blower 83, rear seat evaporator temperature sensor 84, and rear seat air mix door 86 have the same configuration and function as the inside / outside air switching device 52, blower 53, evaporator temperature sensor 54, and air mix door 56, respectively, so detailed explanations are omitted.

[0377] In this embodiment, the refrigeration cycle device 10 has a refrigerant passage that circulates the refrigerant to the rear seat air conditioning unit 80. In addition, the high temperature side heat medium circuit 30 has a high temperature side heat medium passage that circulates the high temperature side heat medium to the rear seat air conditioning unit 80.

[0378] 15, the refrigerant passage connected to one outlet of the refrigerant branching section 18 branches midway. The inlet side of the first expansion valve 17a is connected to the refrigerant passage on one side of the branch. The inlet side of the third expansion valve 17c is connected to the refrigerant passage on the other side of the branch.

[0379] The outlet of the first expansion valve 17a is connected to the refrigerant inlet side of the front evaporator 14a. The refrigerant outlet side of the front evaporator 14a is connected to a front air conditioning inlet pipe 11d that guides the refrigerant flowing out from the front evaporator 14a to the connection device 200. The refrigerant flow downstream side of the front air conditioning inlet pipe 11d is inserted into a serial inlet 221 of the connection device 200, which will be described later.

[0380] The third expansion valve 17c is a rear seat pressure reducing section that reduces the pressure of the refrigerant flowing out from the refrigerant passage of the water-refrigerant heat exchanger 13 and adjusts the flow rate of the refrigerant flowing out downstream during an operation mode that mainly cools the space in which the rear seats are installed. The third expansion valve 17c has a basic configuration similar to that of the first expansion valve 17a and the second expansion valve 17b. The outlet of the third expansion valve 17c is connected to the refrigerant inlet side of the rear seat evaporator 14b. The refrigerant outlet side of the rear seat evaporator 14b is connected to the rear seat inlet pipe 11e that guides the refrigerant flowing out from the rear seat evaporator 14b to the connection device 200. The downstream side of the refrigerant flow of the rear seat inlet pipe 11e is inserted into a second inclined inlet 241 of the connection device 200, which will be described later.

[0381] In this embodiment, the front seat air conditioning inlet pipe 11d functions as a first air conditioning inlet pipe, and the rear seat inlet pipe 11e functions as a second air conditioning inlet pipe. The front seat air conditioning inlet pipe 11d corresponds to the air conditioning inlet pipe 11a in the second embodiment.

[0382] In this embodiment, the rear seat inlet pipe 11e is a refrigerant pipe having an outer diameter smaller than that of the front seat air conditioning inlet pipe 11d and the compressor outlet pipe 11c, and the same outer diameter as that of the cooling section inlet pipe 11b, with an outer diameter of 15.88 mm from the inlet side to the outlet side.

[0383] Further, the rear inflow pipe 11e is provided with a fourth refrigerant temperature sensor 19g for detecting the temperature of the refrigerant flowing out from the rear evaporator 14b and a fourth refrigerant pressure sensor 19h for detecting the pressure of the refrigerant flowing out from the rear evaporator 14b. Further, the rear inflow pipe 11e is provided with a rear evaporation pressure regulating valve 15a for regulating the pressure of the refrigerant flowing out from the rear evaporator 14b.

[0384] The fourth refrigerant temperature sensor 19g, the fourth refrigerant pressure sensor 19h, and the rear seat evaporation pressure control valve 15a have the same configuration and function as the second refrigerant temperature sensor 19b, the second refrigerant pressure sensor 19e, and the evaporation pressure control valve 15, respectively, so detailed explanations are omitted.

[0385] In the connection device 200 of this embodiment, as shown in Figures 16 and 17, a second inclined upstream flow path section 240 is added to allow the refrigerant flowing out of the rear seat evaporator 14b and through the rear seat inlet pipe 11e to flow into the inside of the housing 210.

[0386] 15, in the high-temperature side heat medium circuit 30, the high-temperature side heat medium passage connected to the other outlet of the high-temperature side flow control valve 33 branches midway. The heat medium inlet side of the heater core 35 is connected to the high-temperature side heat medium passage on one side of the branch. The heat medium inlet side of the rear seat heater core 88 is connected to the high-temperature side heat medium passage on the other side of the branch.

[0387] Further, the other branched high-temperature side heat medium passage is provided with a third high-temperature side heat medium temperature sensor 37c that detects the temperature of the high-temperature side heat medium before it flows into the rear heater core 88. The third high-temperature side heat medium temperature sensor 37c transmits a detection signal to the control device 70 in accordance with the temperature of the high-temperature side heat medium that flows out of the high-temperature side flow control valve 33 and before it flows into the rear heater core 88.

[0388] The refrigeration cycle device 10 thus configured cools the interior of the vehicle cabin by cooling the blown air and blowing it out into the space where the driver's seat is located and the space where the rear seats are located, but can also be operated in an all-seat cooling mode that does not cool the battery 60. Furthermore, the refrigeration cycle device 10 can be operated in an all-seat cooling mode that cools the interior of the vehicle cabin by cooling the blown air and blowing it out into the space where the driver's seat is located and the space where the rear seats are located, and also cools the battery 60. Hereinafter, the operation of the all-seat cooling mode will be described as an example of an operation mode that can be performed by the refrigeration cycle device 10 of this embodiment.

[0389] In the front seat cooling mode, the control device 70 switches the refrigeration cycle device 10 to a refrigerant circuit for the all-seat cooling mode. Specifically, the control device 70 operates each component device in the above-mentioned cooling mode, and also throttles the third expansion valve 17c. Based on detection signals transmitted from the fourth refrigerant temperature sensor 19g and the fourth refrigerant pressure sensor 19h, the control device 70 determines the opening degree of the third expansion valve 17c so that the degree of superheat of the refrigerant on the outlet side of the rear seat evaporator 14b becomes a predetermined target degree of superheat.

[0390] Therefore, in the refrigeration cycle device 10 in the all-seat cooling mode, the refrigerant flows in the order of the compressor 12 → the water-refrigerant heat exchanger 13 → the refrigerant branching section 18. One of the refrigerants branched at the refrigerant branching section 18 flows in the order of the first expansion valve 17a → the front seat evaporator 14a → the front seat air conditioning inlet pipe 11d → the connection device 200, and also flows in the order of the third expansion valve 17c → the rear seat evaporator 14b → the rear seat inlet pipe 11e → the connection device 200.

[0391] The refrigerant that flows into the connection device 200 from the front air conditioning inlet pipe 11d and the rear inlet pipe 11e joins together inside the connection device 200 and flows to the compressor 12 via the compressor outlet pipe 11c.

[0392] The other refrigerant branched at the refrigerant branch section 18 flows in the order of the second expansion valve 17b, the chiller 16, the cooling section inlet pipe 11b, the connection device 200, the compressor outlet pipe 11c, and the compressor 12.

[0393] In the all-seat cooling mode, the high-temperature side heat medium flows in the high-temperature side heat medium circuit 30, as in the cooling and cooling mode. In the all-seat cooling mode, the low-temperature side heat medium flows in the low-temperature side heat medium circuit 40, as in the cooling and cooling mode.

[0394] Thus, in the all-seat cooling mode, the refrigerant flowing out from the front evaporator 14a flows into the connection device 200 from the serial inlet 221 via the front air-conditioning inlet piping 11d. Also, the refrigerant flowing out from the rear evaporator 14b flows into the connection device 200 from the second inclined inlet 241 via the rear inlet piping 11e. Furthermore, the refrigerant flowing out from the chiller 16 flows into the connection device 200 from the inclined inlet 231 via the cooling unit inlet piping 11b. Then, the connection device 200 causes the refrigerant flowing in from the serial inlet 221, the second inclined inlet 241, and the inclined inlet 231 to flow out from the serial outlet 253 and guide it to the compressor outlet piping 11c.

[0395] In the refrigeration cycle apparatus 10 in the front seat cooling mode, in addition to the operation in the cooling mode, the third expansion valve 17c reduces the pressure of the refrigerant flowing out from the water-refrigerant heat exchanger 13. In the refrigeration cycle apparatus 10, the rear seat evaporator 14b absorbs heat from the blown air blown from the rear seat blower 83 to evaporate the refrigerant, thereby cooling the blown air.

[0396] Therefore, in the vehicle air conditioner 1 in the all-seat cooling mode, the ventilation air cooled by the front seat evaporator 14a is blown into the space where the driver's seat is located, thereby cooling the space where the driver's seat is located. Also, in the vehicle air conditioner 1 in the all-seat cooling mode, the ventilation air cooled by the rear seat evaporator 14b is blown into the space where the rear seats are located, thereby cooling the space where the rear seats are located.

[0397] Furthermore, the low-temperature side heat medium cooled by the chiller 16 is circulated to cool the battery 60. In the vehicle air conditioner 1 in the cooling mode, the low-temperature side heat medium cooled by the low-temperature side radiator 43 is circulated through the low-temperature side heat medium circuit 40 to cool the inverter 61, the motor generator 62, and the transaxle device 63.

[0398] Next, details of the connection device 200 of this embodiment will be described with reference to Figures 16 and 17. As shown in Figures 16 and 17, compared to the second embodiment, a second inclined upstream path section 240 is added inside the housing 210 as a refrigerant path, the second inclined upstream path section 240 extending from the surface of the left side section 214 toward the bottom side section 212 without penetrating all the way to the bottom side section 212.

[0399] The second inclined upper flow path section 240 extends from a portion of the surface of the left side section 214 that is below the center in the up-down direction DR1 toward a portion to the right of the center in the left-right direction DR3 of the bottom side section 212. In addition, of both ends of the second inclined upper flow path section 240, an intermediate portion of the refrigerant passage different from the both ends of the series downstream flow path section 250 is connected to the end opposite to the side positioned on the surface of the left side section 214.

[0400] That is, in this embodiment, the second inclined upstream section 240 is not directly connected to the series upstream section 220 and the inclined upstream section 230. Specifically, the portion of the series downstream section 250 to which the second inclined upstream section 240 is connected is downstream in the refrigerant flow direction from the portion to which the series upstream section 220 and the inclined upstream section 230 are connected to the series downstream section 250. For this reason, the refrigerant flowing through the second inclined upstream section 240 does not directly merge with the refrigerant flowing through the series upstream section 220 and the inclined upstream section 230.

[0401] The second inclined upstream path section 240 forms a refrigerant passage for guiding the refrigerant flowing out from the rear seat inlet pipe 11e to the inside of the housing 210. The second inclined upstream path section 240 extends linearly along a direction different from the directions in which the serial upstream path section 220, the inclined upstream path section 230, and the serial downstream path section 250 extend. The second inclined upstream path section 240 has a second inclined inlet port 241 communicating with the rear seat inlet pipe 11e on the upstream side of the refrigerant flow, and a second inclined junction port 242 communicating with the serial downstream path section 250 on the downstream side of the refrigerant flow. The direction in which the second inclined upstream path section 240 extends will be described later.

[0402] The second inclined upstream section 240 is formed such that a seventh inner diameter φ7, which is the inner diameter of the second inclined upstream section 240, is slightly larger than the outer diameter of the rear seat inlet pipe 11e. The second inclined upstream section 240 is formed such that the rear seat inlet pipe 11e can be inserted into the second inclined upstream section 240 from the second inclined inlet 241. Specifically, the inner diameter of the second inclined upstream section 240 is formed slightly larger than the outer diameter 15.88 mm of the rear seat inlet pipe 11e.

[0403] The second inclined upper passage section 240 is formed so that the seventh inner diameter φ7 is uniform from the upstream side of the refrigerant flow to the downstream side of the refrigerant flow. The seventh inner diameter φ7 is the diameter of a cross-sectional shape in a direction perpendicular to the extension direction of the second inclined upper passage section 240. In this embodiment, the second inclined upper passage section 240 is formed so that the seventh inner diameter φ7 is smaller than the fourth inner diameter φ4 and the sixth inner diameter φ6 and is equal to the fifth inner diameter φ5.

[0404] In addition, the series downstream passage section 250 of this embodiment has a downstream junction section 252, downstream in the refrigerant flow direction from the multiple junction section 251, that joins the refrigerant flowing through the second inclined upstream passage section 240 to the series downstream passage section 250.

[0405] Here, the portion where a straight line L4 passing through the center of the serial outlet 253 and extending along the direction in which the serial downstream flow path section 250 extends intersects with a straight line L7 passing through the center of the second inclined inlet 241 and extending along the direction in which the second inclined upstream flow path section 240 extends is defined as the downstream confluence section 252.

[0406] In the present embodiment, in the series downstream path section 250, the position where the series upstream path section 220 and the inclined upstream path section 230 join and the position where the second inclined upstream path section 240 join are provided at positions different from each other. The refrigerant flowing through the series upstream path section 220 and the inclined upstream path section 230 flows into the multiple junction section 251. The refrigerant that has flowed into the series downstream path section 250 from the series upstream path section 220 and the inclined upstream path section 230 and the refrigerant flowing through the second inclined upstream path section 240 flow into the downstream side junction section 252. In the present embodiment, the multiple junction section 251 and the downstream side junction section 252 function as junction sections.

[0407] The serial downstream passage section 250 has a sixth inner diameter φ6 larger than a seventh inner diameter φ7. That is, the serial downstream passage section 250 has an inner diameter on the downstream side of the downstream junction section 252 in the refrigerant flow direction larger than the inner diameter of the second inclined upstream passage section 240.

[0408] In other words, the serial downstream channel section 250 is formed such that the flow path cross-sectional area of ​​a cross section perpendicular to the refrigerant flow direction, downstream of the downstream junction 252, is larger than the flow path cross-sectional area of ​​a cross section perpendicular to the refrigerant flow direction in the second inclined upstream channel section 240. The serial outlet 253 is positioned vertically lower than the second inclined inlet 241.

[0409] Next, the direction in which the second inclined upstream section 240 extends will be described in detail with reference to a predetermined merging reference direction DRC. The predetermined merging reference direction DRC is a direction going upward along the vertical direction DR1, and is a direction going upward along the vertical direction DR1 with the multiple merging sections 251 and the downstream merging section 252 as references.

[0410] The second inclined upstream section 240 extends at a fourth angle θ4 greater than 0° and smaller than 90° with respect to a predetermined junction reference direction DRC with respect to the downstream junction 252 as a reference. Here, the angle extending from the downstream junction 252 with respect to the predetermined junction reference direction DRC is an angle in which the upper side of the up-down direction DR1 is set to 0° and the counterclockwise direction is set to the positive direction in the cross-sectional view shown in Fig. 17. The fourth angle θ4 is an angle formed by the predetermined junction reference direction DRC and the direction in which the second inclined upstream section 240 extends with the downstream junction 252 as a center.

[0411] In this embodiment, the second inclined upstream passage section 240 extends so that the fourth angle θ4 is the same angle as the third angle θ3, i.e., 45°. Thus, the direction in which the second inclined upstream passage section 240 of this embodiment extends includes the left-right direction DR3 and the up-down direction DR1, but does not include the front-rear direction DR2. Note that the fourth angle θ4 may be an angle larger than the third angle θ3 or smaller than the third angle θ3, as long as it is within a range of a magnitude larger than 0° and smaller than 90°.

[0412] Next, the flow and pressure loss of the refrigerant flowing inside the connection device 200 of this embodiment when the refrigeration cycle apparatus 10 is operated in the all-seat cooling mode will be described with reference to FIG.

[0413] In the all-seat cooling mode, the refrigerant flows into the connection device 200 from the serial inlet 221 via the front seat air conditioning inlet piping 11d. The refrigerant also flows into the connection device 200 from the inclined inlet 231 via the cooling section inlet piping 11b. The refrigerant also flows into the connection device 200 from the second inclined inlet 241 via the rear seat inlet piping 11e.

[0414] 18, the refrigerant flowing in from the serial inlet 221 flows downward in the up-down direction DR1 along the direction in which the serial upstream path section 220 extends, and flows into the serial downstream path section 250 from the serial junction port 222. Meanwhile, the refrigerant flowing in from the inclined inlet 231 flows along the direction in which the inclined upstream path section 230 extends, and flows into the serial downstream path section 250 from the inclined junction port 232, as shown by the refrigerant flow F8 in FIG.

[0415] The refrigerant flowing into the series downstream flow path section 250 from the series junction port 222 and the inclined junction port 232 merges and collides with each other, and then flows downward in the vertical direction DR1 toward the downstream junction port 252 along the direction in which the series downstream flow path section 250 extends.

[0416] The refrigerant that flows into the series downstream path section 250 from the series junction port 222 flows toward the downstream side of the refrigerant flow without changing its flow direction when it flows into the series downstream path section 250. In contrast, the refrigerant that flows into the series downstream path section 250 from the inclined junction port 232 flows toward the downstream side of the refrigerant flow with its flow direction changed by 45°, which is the third angle θ3, when it flows into the series downstream path section 250.

[0417] The flow velocity vector of the refrigerant flowing from the multiple junction 251 toward the downstream junction 252 has a downward flow velocity vector component in the up-down direction DR1, and has no flow velocity vector components in other directions. That is, in the serial downstream path section 250, the flow velocity vector of the refrigerant flowing upstream of the downstream junction 252 and immediately before flowing into the downstream junction 252 has a downward flow velocity vector component in the up-down direction DR1, and has no flow velocity vector components in other directions.

[0418] In addition, the refrigerant flowing in from the second inclined inlet 241 flows along the extension direction of the second inclined upstream flow path section 240, as shown by refrigerant flow F9 in Figure 18, and flows into the serial downstream flow path section 250 from the second inclined junction port 242.

[0419] The flow velocity vector of the refrigerant flowing along the extension direction of the second inclined upper flow path section 240 has a downward flow velocity vector component in the up-down direction DR1 and a rightward flow velocity vector component in the left-right direction DR3, but has no flow velocity vector component in the front-rear direction DR2. That is, the flow velocity vector of the refrigerant flowing through the second inclined upper flow path section 240 and immediately before flowing into the downstream junction 252 has a downward flow velocity vector component in the up-down direction DR1 and a rightward flow velocity vector component in the left-right direction DR3, but has no flow velocity vector in the front-rear direction DR2.

[0420] The refrigerant flowing from the second inclined junction port 242 into the serial downstream path section 250 merges with and collides with the refrigerant flowing from the serial junction port 222 and the inclined junction port 232 into the serial downstream path section 250. When the refrigerant flowing from the second inclined junction port 242 into the serial downstream path section 250 flows into the serial downstream path section 250, its flow direction is changed by 45°, which is the fourth angle θ4, and the refrigerant flows toward the downstream side of the refrigerant flow.

[0421] Thereafter, the refrigerant that flows into the serial downstream flow path section 250 from each of the serial inlet 221, the inclined inlet 231, and the second inclined inlet 241 flows downward in the vertical direction DR1 from the downstream junction section 252, and flows out from the serial outlet 253 to the compressor outflow pipe 11c.

[0422] As described above, in the connection device 200 of this embodiment, the shape of the housing 210 and the shape of the refrigerant passage formed inside the housing 210 are different from those of the second embodiment. The rest of the configuration and operation of the connection device 200 are the same as those of the second embodiment. This makes it possible to obtain the same effects as those of the first embodiment.

[0423] The refrigerant flowing from the second inclined junction port 242 into the serial downstream path section 250 merges with and collides with the refrigerant flowing from the serial junction port 222 and the inclined junction port 232 into the serial downstream path section 250, and the flow direction of the refrigerant is changed by 45°. The refrigerant flowing from the second inclined junction port 242 into the serial downstream path section 250 flows downward in the up-down direction DR1 together with the refrigerant flowing from the serial junction port 222 and the inclined junction port 232.

[0424] Therefore, in the connection device 200 of this embodiment, the change in the flow direction of the refrigerant can be made smaller than when the second inclined upstream section 240 extends at an angle of 90° from the predetermined merging reference direction DRC. Therefore, the pressure loss caused when the flow direction of the refrigerant changes can be suppressed.

[0425] Furthermore, in the connection device 200 of this embodiment, the refrigerant flowing from the multiple junction 251 toward the downstream junction 252 does not include a flow velocity vector in a direction opposite to that of the refrigerant flowing from the second inclined upstream passage section 240 into the serial downstream passage section 250. Therefore, compared to a case without such a configuration, it is possible to suppress pressure loss due to collisions when the refrigerant flows from the second inclined upstream passage section 240 to the serial downstream passage section 250.

[0426] (1) In the above embodiment, the inner diameter of the series downstream passage section 250 downstream of the downstream junction section 252 in the refrigerant flow direction is larger than the inner diameter of the second inclined upstream passage section 240 .

[0427] Therefore, in the series downstream flow path section 250, the flow velocity of the refrigerant flowing downstream of the downstream junction 252 is slower than when the inner diameter of the refrigerant flow downstream of the downstream junction 252 is equal to or smaller than the inner diameter of the second inclined upper flow path section 240. Therefore, compared to when the inner diameter of the series downstream flow path section 250 is equal to or smaller than the inner diameter of the second inclined upper flow path section 240, pressure loss generated when the refrigerant flows through the series downstream flow path section 250 can be suppressed.

[0428] (2) In the above embodiment, the connection device 200 is configured so that the serial upstream passage portion 220 is connected to the front air conditioning inlet pipe 11d.

[0429] Here, the vehicle air conditioner 1 mounted on the electric vehicle places more importance on conditioning the vehicle interior than on cooling the battery 60. Also, the vehicle air conditioner 1 places more importance on conditioning the space in the vehicle interior where the driver's seat is located than on the space in the rear seats. Also, the vehicle air conditioner 1 places more importance on cooling the battery 60 than on conditioning the space in the rear seats.

[0430] For this reason, in the refrigeration cycle apparatus 10 operating in the all-seat cooling mode, it is necessary to flow more refrigerant into the front air-conditioning inlet pipe 11d than into the cooling section inlet pipe 11b, and more refrigerant into the cooling section inlet pipe 11b than into the rear inlet pipe 11e. In this case, the largest amount of refrigerant flows into the series upstream path section 220 among the three upstream path sections 220, 230, and 240 in the connection device 200. In the entire refrigeration cycle apparatus 10, the pressure loss occurring when merging with the series downstream path section 250 has a greater effect on the series upstream path section 220, the inclined upstream path section 230, and the second inclined upstream path section 240, in that order.

[0431] In the above embodiment, the front seat air conditioning inlet pipe 11d is connected to the serial upstream path section 220, in which the flow direction of the refrigerant does not change, among the three upstream path sections 220, 230, 240. Therefore, when the refrigerant from each of the three upstream path sections 220, 230, 240 joins the serial downstream path section 250, it is easy to suppress the pressure loss caused when the flow direction of the refrigerant changes in the refrigeration cycle apparatus 10 as a whole. Therefore, when the largest amount of refrigerant flows through the front seat air conditioning inlet pipe 11d, the pressure loss in the entire refrigeration cycle apparatus 10 can be suppressed compared to a case not configured in this way.

[0432] (3) In the above embodiment, the multiple junctions 251 and the downstream junction 252 are provided at different positions in the serial downstream path section 250. Therefore, when the three upstream path sections 220, 230, 240 join in the serial downstream path section 250, the position where the serial upstream path section 220 and the inclined upstream path section 230 join can be shifted from the position where the second inclined upstream path section 240 joins.

[0433] Therefore, when the refrigerant flows from the upstream flow paths 220, 230 connected to the multiple junctions 251 into the series downstream flow path section 250, it is possible to avoid collision with the refrigerant merging from the second inclined upstream flow path section 240. As a result, it is possible to suppress pressure loss due to collision when the refrigerant merges in the series downstream flow path section 250, compared to a case not configured in this way.

[0434] (4) In the above embodiment, in the connection device 200, the front seat air conditioning inlet pipe 11d is connected to the serial upstream passage section 220, and the cooling section inlet pipe 11b is connected to the inclined upstream passage section 230. In addition, in the connection device 200, the rear seat inlet pipe 11e is connected to the second inclined upstream passage section 240. The multiple junction section 251 is provided at a position upstream of the downstream junction section 252 in the refrigerant flow direction.

[0435] As described above, in the series downstream path section 250, when there is a refrigerant passage that merges with a refrigerant passage midway from the upstream side to the downstream side of the refrigerant flow in the series downstream path section 250, a force is generated that draws the refrigerant flowing from the merging refrigerant passage into the series downstream path section 250. The force that draws the refrigerant into the series downstream path section 250 becomes larger as the flow of refrigerant flowing through the series downstream path section 250 increases.

[0436] Furthermore, in the refrigeration cycle device 10 operating in the all-seat cooling mode, more refrigerant flows into the inclined upstream flow path section 230 than into the second inclined upstream flow path section 240, and more refrigerant flows into the series upstream flow path section 220 than into the inclined upstream flow path section 230.

[0437] In the above embodiment, the multiple confluence portion 251 is provided at a position upstream of the downstream confluence portion 252 in the refrigerant flow. Therefore, the refrigerant flowing through the second inclined upper flow path portion 240 merges with the serial downstream flow path portion 250 through which the refrigerant flowing from the serial upstream flow path portion 220 and the inclined upper flow path portion 230 flows. Therefore, in the serial downstream flow path portion 250, the flow rate of the refrigerant flowing upstream of the downstream confluence portion 252 can be increased compared to a case not configured in this way. Therefore, the force of the refrigerant flowing through the serial downstream flow path portion 250 to draw the refrigerant from the second inclined confluence port 242 into the serial downstream flow path portion 250 can be increased, so that the pressure loss when the flow direction of the refrigerant changes can be suppressed. (First modified example of the third embodiment) In the above-described third embodiment, the third angle θ3 and the fourth angle θ4 are configured to be the same, but the present invention is not limited to this. For example, the inclined upstream passage section 230 may be configured so that the third angle θ3 is smaller than the fourth angle θ4.

[0438] According to this, the amount of change in the flow direction of the refrigerant when it merges from the inclined upstream path section 230 to the series downstream path section 250 is smaller than when it merges from the second inclined upstream path section 240 to the series downstream path section 250. Therefore, compared to the pressure loss when the flow direction of the refrigerant changes when it merges from the second inclined upstream path section 240 to the series downstream path section 250, the pressure loss when the flow direction of the refrigerant changes when it merges from the inclined upstream path section 230 to the series downstream path section 250 can be suppressed.

[0439] Furthermore, in the case where more refrigerant flows through the cooling section inlet pipe 11b than through the rear inlet pipe 11e, the pressure loss in the entire refrigeration cycle apparatus 10 can be suppressed compared to a case where such a configuration is not used. (Second modified example of the third embodiment) In the above-described third embodiment, an example has been described in which the inner diameter of the serial downstream path section 250 and the inner diameter of the serial upstream path section 220 are formed to be the same size, but the present invention is not limited to this. For example, when the outer diameter of the front seat air conditioning inlet pipe 11d is the same as the outer diameter of the rear seat inlet pipe 11e and the outer diameter of the cooling section inlet pipe 11b, the inner diameter of the serial upstream path section 220 may be formed to be smaller than the inner diameter of the serial downstream path section 250. Specifically, the inner diameter of the serial upstream path section 220 may be the same as the inner diameters of the inclined upper path section 230 and the second inclined upper path section 240. (Third modified example of the third embodiment) In the above-described third embodiment, an example has been described in which the inner diameter of the serial downstream path section 250 is equal from the most upstream part of the refrigerant flow through the multiple junction section 251 and the downstream junction section 252 to the serial outlet 253. However, the present invention is not limited to this. For example, as shown in Fig. 19, the serial downstream path section 250 may be configured such that the inner diameter increases stepwise from the most upstream part of the refrigerant flow through the multiple junction section 251 and the downstream junction section 252 to the serial outlet 253. Specifically, the serial downstream path section 250 may be configured such that the inner diameter of the portion where the multiple junction section 251 is provided is larger than that of the most upstream part of the refrigerant flow, and the inner diameter of the portion where the downstream junction section 252 is provided is larger than that of the portion where the multiple junction section 251 is provided.

[0440] As a result, the flow velocity of the refrigerant in the series downstream path section 250 decreases as the inner diameter increases. Therefore, in the series downstream path section 250, the pressure loss that occurs when the refrigerant flows through the series downstream path section 250 can be suppressed compared to a case not configured in this way. (Fourth Modification of the Third Embodiment) In the above-mentioned third embodiment, the outer diameters of the front seat air conditioning inlet pipe 11d, the cooling section inlet pipe 11b, and the rear seat inlet pipe 11e are equal from the inlet side to the outlet side, but the present invention is not limited to this. For example, as shown in FIG. 20, the front seat air conditioning inlet pipe 11d may be formed so that the outer diameter of the flow path increases from the upstream side of the refrigerant flow to the downstream side of the refrigerant flow, and the outlet side is inserted into the serial upper flow path section 220. The cooling section inlet pipe 11b may be formed so that the outer diameter of the flow path increases from the upstream side of the refrigerant flow to the downstream side of the refrigerant flow, and the outlet side is inserted into the inclined upper flow path section 230. The rear seat inlet pipe 11e may be formed so that the outer diameter of the flow path increases from the upstream side of the refrigerant flow to the downstream side of the refrigerant flow, and the outlet side is inserted into the second inclined upper flow path section 240.

[0441] As a result, in the front seat air conditioning inflow pipe 11d, the flow speed of the refrigerant flowing downstream of the portion where the outer diameter is larger is slower than the flow speed of the refrigerant flowing upstream of the portion where the outer diameter is larger. Also, in the cooling section inflow pipe 11b, the flow speed of the refrigerant flowing downstream of the portion where the outer diameter is larger is slower than the flow speed of the refrigerant flowing upstream of the portion where the outer diameter is larger. Also, in the rear seat inflow pipe 11e, the flow speed of the refrigerant flowing downstream of the portion where the outer diameter is larger is slower than the flow speed of the refrigerant flowing upstream of the portion where the outer diameter is larger.

[0442] Therefore, compared to a case not configured in this manner, it is possible to suppress pressure losses that occur when the refrigerant flows through the front seat air conditioning inlet pipe 11d, the cooling section inlet pipe 11b, and the rear seat inlet pipe 11e.

[0443] (Fourth embodiment) Next, a fourth embodiment will be described with reference to Fig. 21. A connection device 300 of this embodiment differs from the second embodiment in the shape of a housing 310. In this embodiment, the parts different from the second embodiment will be mainly described, and the description of the parts similar to the second embodiment may be omitted.

[0444] In the present embodiment, the housing 310 is formed by connecting a plurality of cylindrical refrigerant passage forming portions. Specifically, the housing 310 is composed of a first cylindrical portion 311 that defines a first cylindrical upstream passage portion 320 and a downstream passage portion 350 therein, and a second cylindrical portion 312 that defines a second cylindrical upstream passage portion 330 therein.

[0445] As shown in Fig. 21, the first cylindrical portion 311 has a hollow cylindrical shape and extends along the vertical direction DR1. The first cylindrical portion 311 has a refrigerant passage formed therein through which the refrigerant flows. The first cylindrical portion 311 is open on both sides in the vertical direction DR1. The first cylindrical portion 311 is configured such that the refrigerant flowing in from one side in the vertical direction DR1 flows through the internal refrigerant passage and can flow out from the other side in the vertical direction DR1. The second cylindrical portion 312 is connected to approximately the center of the outer periphery of the first cylindrical portion 311 in the vertical direction DR1.

[0446] The second cylindrical portion 312 has a hollow cylindrical shape and extends from a portion connected to the first cylindrical portion 311 at an angle toward the upper side in the vertical direction DR1 and toward the right side in the horizontal direction DR3. A refrigerant passage through which a refrigerant flows is formed inside the second cylindrical portion 312. The second cylindrical portion 312 is open on both sides in the direction in which the second cylindrical portion 312 extends. The refrigerant passage inside the second cylindrical portion 312 communicates with the refrigerant passage inside the first cylindrical portion 311 via the opening side on the side connected to the first cylindrical portion 311.

[0447] In this embodiment, the connection device 300 has a first cylindrical upstream flow path section 320 and a cylindrical downstream flow path section 350 inside the first cylindrical section 311. Of the refrigerant passages formed inside the first cylindrical section 311, the first cylindrical upstream flow path section 320 is a section from the upper end in the vertical direction DR1 to a section that communicates with the refrigerant passage of the second cylindrical section 312. The first cylindrical upstream flow path section 320 corresponds to the serial upstream flow path section 220 of the second embodiment. In this embodiment, the first cylindrical upstream flow path section 320 functions as a serial upstream side flow path section.

[0448] Moreover, among the refrigerant passages formed inside the first cylindrical portion 311, a portion from a portion communicating with the refrigerant passage of the second cylindrical portion 312 to a lower end portion in the up-down direction DR1 constitutes a downstream-tube flow path portion 350. The downstream-tube flow path portion 350 corresponds to the in-line downstream flow path portion 250 of the second embodiment. In this embodiment, the downstream-tube flow path portion 350 functions as a downstream side flow path portion.

[0449] That is, of the refrigerant passages formed inside the first cylindrical portion 311, a portion above approximately the center in the vertical direction DR1 is configured as a first cylindrical upper flow path portion 320 that allows the refrigerant to flow into the connection device 300. Also, of the refrigerant passages formed inside the first cylindrical portion 311, a portion below approximately the center in the vertical direction DR1 is configured as a cylindrical lower flow path portion 350 that allows the refrigerant to flow out of the connection device 300.

[0450] In this embodiment, the connection device 300 has a second cylindrical upstream flow path section 330 inside the second cylindrical section 312. The second cylindrical upstream flow path section 330 corresponds to the inclined upstream flow path section 230 of the second embodiment. That is, a refrigerant passage formed inside the second cylindrical section 312 is configured as the second cylindrical upstream flow path section 330 that causes the refrigerant to flow into the connection device 300. In this embodiment, the second cylindrical upstream flow path section 330 functions as an inclined upstream side flow path section.

[0451] The first cylindrical upstream path section 320 extends linearly in the direction in which the first cylindrical section 311 extends, i.e., in the vertical direction DR1. The first cylindrical upstream path section 320 has a first cylindrical inlet 321 to which the air conditioning inlet pipe 11a is connected at an upper end in the vertical direction DR1, and an upper end in the vertical direction DR1 of the cylindrical downstream path section 350 is connected to a lower end in the vertical direction DR1.

[0452] The second cylindrical upstream flow path section 330 extends in a direction in which the second cylindrical section 312 extends, i.e., inclined toward the upper side in the vertical direction DR1 and toward the right side in the horizontal direction DR3. The second cylindrical upstream flow path section 330 has an upper end of the cylindrical downstream flow path section 350 connected to an end of the second cylindrical upstream flow path section 330 that is connected to the refrigerant passage of the first cylindrical section 311, among both ends. The second cylindrical upstream flow path section 330 has a second cylindrical inlet 331 to which the cooling section inlet pipe 11b is connected, at an end opposite to the end that is connected to the refrigerant passage of the first cylindrical section 311, among both ends.

[0453] The downstream passage 350 extends linearly in the direction in which the first cylindrical portion 311 extends, i.e., in the vertical direction DR1. The downstream passage 350 has an upper end in the vertical direction DR1 to which the first upstream passage 320 and the second upstream passage 330 are connected, and has a cylindrical outlet 353 to which the compressor outlet pipe 11c is connected, at a lower end in the vertical direction DR1.

[0454] The downstream pipe section 350 has a cylindrical junction section 351 on the upstream side of the refrigerant flow that merges the refrigerant flowing through the first upstream pipe section 320 and the second upstream pipe section 330 into the downstream pipe section 350. In this embodiment, the cylindrical junction section 351 functions as a junction section.

[0455] In this manner, the first cylindrical upstream passage section 320 and the second cylindrical upstream passage section 330 are connected to each other at their ends on the side where the respective down-tube passage sections 350 are connected. That is, the most downstream refrigerant flow portion of the first cylindrical upstream passage section 320 and the most downstream refrigerant flow portion of the second cylindrical upstream passage section 330 are directly connected to the most upstream refrigerant flow portion of the down-tube passage section 350.

[0456] The first cylindrical upstream flow path section 320 extends along a predetermined merging reference direction DRC. Therefore, the angle formed by the predetermined merging reference direction DRC and the direction in which the first cylindrical upstream flow path section 320 extends, centered on the cylindrical merging section 351, is 0°. In contrast, the second cylindrical upstream flow path section 330 extends at an angle of 45° from the predetermined merging reference direction DRC.

[0457] As described above, in the connection device 300 of this embodiment, the shape of the housing 310 is different from that of the second embodiment. The rest of the configuration and operation of the connection device 300 are the same as those of the second embodiment. As a result, it is possible to obtain the same effects as those of the second embodiment.

[0458] (Other embodiments) Representative embodiments of the present disclosure have been described above, but the present disclosure is not limited to the above-described embodiments and can be modified in various ways, for example, as described below.

[0459] In the above-mentioned embodiment, the connection device 100, 200, 300 is configured to merge the refrigerant flowing in from a plurality of refrigerant pipes and guide it to one refrigerant pipe, but the present invention is not limited to this. For example, as shown in Fig. 22, the connection device 500 may be configured to branch the refrigerant flowing in from one refrigerant pipe inside the connection device 500 and to flow out to a plurality of refrigerant pipes.

[0460] For example, when a connection device 500 is arranged in place of the refrigerant branching section 18 in the refrigeration cycle apparatus 10, the connection device 500 may be configured to branch the refrigerant flowing in from the water-refrigerant heat exchanger 13 and guide it to the first expansion valve 17a and the second expansion valve 17b.

[0461] 22, an upstream flow path section 510 connected to a refrigerant piping that guides the refrigerant flowing out from the outlet side of the refrigerant passage of the water-refrigerant heat exchanger 13 to the connection device 500 is provided inside the connection device 500. Also provided inside the connection device 500 are a downstream flow path section 520 connected to a refrigerant piping that guides the refrigerant that has flowed into the connection device 500 to the inlet side of the first expansion valve 17a, and a downstream flow path section 530 connected to a refrigerant piping that guides the refrigerant that has flowed into the connection device 500 to the inlet side of the second expansion valve 17b.

[0462] Here, a portion where the refrigerant that has flowed into the upstream channel section 510 branches is referred to as a branch section 540, and a direction in which the upstream channel section 510 extends from the branch section 540 toward the upstream side of the refrigerant flow of the upstream channel section 510 is referred to as an upstream direction. A direction opposite to the upstream direction is referred to as a predetermined branch reference direction DRC2. In this case, the downstream channel section 520 and the downstream channel section 530 extend at an angle greater than 0° and less than 90° with respect to the predetermined branch reference direction DRC2.

[0463] This makes it possible to reduce the amount of change in the flow direction of the refrigerant compared to when the downstream flow path section 520 and the downstream flow path section 530 extend at an angle of 90° relative to the predetermined branch reference direction DRC2, thereby suppressing pressure loss when the flow direction of the refrigerant changes.

[0464] In the above-described embodiment, the number of upstream flow passages formed inside the connection device 100, 200, 300 is two or three, but the present invention is not limited to this. For example, the connection device 100, 200, 300 may have four or more upstream flow passages formed inside.

[0465] In the above embodiment, an example has been described in which the steep upward flow path section 120 and the low upward flow path section 130 formed in the connection device 100 extend at an angle greater than 0° and less than 90° with respect to the predetermined merging reference direction DRC, but the present invention is not limited to this. For example, of the steep upward flow path section 120 and the low upward flow path section 130 formed in the connection device 100, one of the upstream flow path sections may extend at an angle greater than 0° and less than 90° with respect to the predetermined merging reference direction DRC. In this case, the other upstream flow path section extends at an angle greater than 0° and less than 90° with respect to the predetermined merging reference direction DRC.

[0466] In the above embodiment, an example has been described in which the inner diameter of the downstream side flow path section 140 is larger than the inner diameter of the steep upward flow path section 120 and the inner diameter of the low upward flow path section 130, but the present invention is not limited to this. Also, an example has been described in which the inner diameter of the serial downstream flow path section 250 is larger than the inner diameter of the inclined upward flow path section 230 and the inner diameter of the second inclined upward flow path section 240, but the present invention is not limited to this.

[0467] For example, the inner diameter of the downstream flow passage section 140 may be smaller than the inner diameter of the steep upstream flow passage section 120 and the inner diameter of the low upstream flow passage section 130. Also, the inner diameter of the serial downstream flow passage section 250 may be smaller than the inner diameter of the inclined upstream flow passage section 230 and the inner diameter of the second inclined upstream flow passage section 240.

[0468] In the above embodiment, the air conditioning inlet pipe 11a is connected to the steep upward flow path section 120, the cooling section inlet pipe 11b is connected to the low upward flow path section 130, and the compressor outlet pipe 11c is connected to the downstream side flow path section 140, but the present invention is not limited to this. In addition, in the above embodiment, the front seat air conditioning inlet pipe 11d is connected to the serial upstream flow path section 220, the cooling section inlet pipe 11b is connected to the inclined upstream flow path section 230, the rear seat inlet pipe 11e is connected to the second inclined upstream flow path section 240, and the compressor outlet pipe 11c is connected to the serial downstream flow path section 250, but the present invention is not limited to this. The refrigerant pipes connected to each of the flow paths 120, 130, 140, 220, 230, 240, and 250 can be changed as appropriate.

[0469] In the above embodiment, an example has been described in which the ratio of the inner diameter of the downstream side flow passage section 140 to the inner diameter of the steep upstream flow passage section 120 and the inner diameter of the low upstream flow passage section 130 is 1.20, but this is not limiting. Also, an example has been described in which the ratio of the inner diameter of the inclined upstream flow passage section 230 and the inner diameter of the second inclined upstream flow passage section 240 to the inner diameter of the serial downstream flow passage section 250 is 1.20, but this is not limiting.

[0470] The ratio of the inner diameter of the downstream side passage section 140 to the inner diameter of the steep upstream passage section 120 and the inner diameter of the low upstream passage section 130 can be changed as appropriate according to the outer diameter of the refrigerant pipes connected to each. Also, the ratio of the inner diameter of the serial downstream passage section 250 to the inner diameter of the inclined upstream passage section 230 and the inner diameter of the second inclined upstream passage section 240 can be changed as appropriate according to the outer diameter of the refrigerant pipes connected to each.

[0471] In the above embodiment, an example has been described in which the refrigerant outlet 143 is positioned vertically lower than the rapid inlet 121 and the low inlet 131, but the present invention is not limited to this. Also, in the above embodiment, an example has been described in which the serial outlet 253 is positioned vertically lower than the serial inlet 221, the inclined inlet 231, and the second inclined inlet 241, but the present invention is not limited to this.

[0472] The connection device 100 may be configured such that the refrigerant outlet 143 is positioned vertically above the rapid inlet 121 and the low inlet 131. The connection device 200 may be configured such that the serial outlet 253 is positioned vertically above the serial inlet 221, the inclined inlet 231, and the second inclined inlet 241.

[0473] In the above-described embodiment, an example has been described in which the inner diameters of the steep upstream passage section 120, the low upstream passage section 130, the serial upstream passage section 220, the inclined upstream passage section 230, and the second inclined upstream passage section 240 are formed to have a size corresponding to the most downstream refrigerant flow portion of the refrigerant pipe to which they are connected, but this is not limiting. Also, in the above-described embodiment, an example has been described in which the inner diameters of the downstream side passage section 140 and the serial downstream passage section 250 are formed to have a size corresponding to the most upstream refrigerant flow portion of the refrigerant pipe to which they are connected, but this is not limiting.

[0474] For example, the inner diameters of the steep upstream passage section 120, the low upstream passage section 130, the series upstream passage section 220, the inclined upstream passage section 230, and the second inclined upstream passage section 240 may be formed to have a size that does not correspond to the most downstream refrigerant flow portion of the refrigerant pipe to which they are connected. Also, the inner diameters of the downstream side passage section 140 and the series downstream passage section 250 may be formed to have a size that does not correspond to the most upstream refrigerant flow portion of the refrigerant pipe to which they are connected.

[0475] In this case, by using a refrigerant piping conversion section having an inlet side outer diameter and an outlet side outer diameter that are different from each other, each upstream path section and each downstream path section can be connected to the refrigerant piping to which it is connected.

[0476] In the above-described embodiment, the refrigerant passages formed inside the connection devices 100, 200, and 300 are formed linearly from the upstream side to the downstream side of the refrigerant flow, but the present invention is not limited to this. For example, the refrigerant passages formed inside the connection devices 100, 200, and 300 may be formed to include a portion formed in a curved shape.

[0477] In the above-described embodiments, it goes without saying that the elements constituting the embodiments are not necessarily essential, except in cases where it is particularly expressly stated that they are essential or where they are clearly considered to be essential in principle.

[0478] In the above-described embodiments, when numerical values ​​such as the number, values, amounts, ranges, etc. of components of the embodiments are mentioned, they are not limited to the specific numbers unless it is specifically stated as required or unless it is clearly limited to a specific number in principle.

[0479] In the above-described embodiments, when referring to the shapes, positional relationships, etc. of components, etc., there is no limitation to those shapes, positional relationships, etc., unless specifically stated or in principle limited to a specific shape, positional relationship, etc. [Explanation of symbols]

[0480] 100 Connection Device 110 Cabinet 120, 130 Upstream flow path section 140 Downstream flow path section 141, 142 Junction

Claims

1. A connection device for connecting a plurality of inlet pipes (11a, 11b, 11d, 11e) and one outlet pipe (11c) in a refrigeration cycle apparatus (10) in which a refrigerant circulates, and guiding the refrigerant flowing in from the plurality of inlet pipes to the outlet pipe provided downstream of the plurality of inlet pipes in the refrigerant flow, A housing (110, 210, 310), a plurality of upstream flow passage portions (120, 130, 220, 230, 240, 320, 330) connected one-to-one to the plurality of inlet pipes and causing the refrigerant to flow into the housing; a downstream flow passage portion (140, 250, 350) that is connected one-to-one to the outflow pipe and communicates with a plurality of the upstream flow passage portions, and causes the refrigerant that has flowed into the inside of the housing to flow out to the outside of the housing; a merging section (141, 142, 251, 252, 351) that merges the refrigerant flowing from the plurality of upstream flow passage sections into the downstream flow passage section, When a direction in which the downstream flow path section extends from the junction section toward the downstream side of the refrigerant flow of the downstream flow path section is defined as a downstream direction, the multiple upstream flow path sections are composed of a first inclined upstream flow path section (120) extending along a direction shifted from the downstream direction by an angle greater than 0° and less than 90°, and a second inclined upstream flow path section (130) extending along a direction different from the direction in which the first inclined upstream flow path section extends and which is shifted from the downstream direction by an angle greater than 0° and less than 90°, The refrigeration cycle device is applied to an air conditioning device for a vehicle, and includes a compressor (12) that compresses and discharges a sucked refrigerant, a heating section (13, 30) that uses the refrigerant discharged from the compressor as a heat source to heat air to be blown to a space to be air-conditioned, an air-conditioning heat exchanger (14) that evaporates the refrigerant flowing out of the heating section to cool the air before it is heated by the heating section, and a cooling section (16, 40) that evaporates the refrigerant flowing out of the heating section to cool a cooling object other than the air to be cooled, The plurality of inlet pipes include an air conditioning inlet pipe (11a) through which the refrigerant flowing out from the air conditioning heat exchanger flows, and a cooling section inlet pipe (11b) through which the refrigerant flowing out from the cooling section flows, The outflow pipe is a compressor outflow pipe (11c) that introduces a refrigerant to the compressor, The first inclined upstream flow path portion is connected to the air conditioning inlet pipe, The second inclined upstream flow path portion is connected to the cooling section inlet pipe, The downstream flow path portion is connected to the compressor outflow pipe, a direction in which the first inclined upstream channel section extends in the downstream direction is smaller than a direction in which the second inclined upstream channel section extends in the downstream direction.

2. 2. The connection device according to claim 1, wherein the inner diameter of the downstream flow passage portion is larger than the inner diameter of the first inclined upstream flow passage portion downstream of the refrigerant flow path from a portion where the first inclined upstream flow passage portion is connected, and the inner diameter of the downstream flow passage portion is larger than the inner diameter of the second inclined upstream flow passage portion downstream of the refrigerant flow path from a portion where the second inclined upstream flow passage portion is connected.

3. The refrigeration cycle device circulates a refrigerant containing oil, By switching the refrigerant circuit through which the refrigerant circulates, the operation mode of the refrigeration cycle device can be switched between an operation mode in which the refrigerant flows through all of the plurality of inlet pipes and an operation mode in which the refrigerant does not flow through at least one of the plurality of inlet pipes, The connection device according to claim 1 or 2, wherein the downstream flow passage portion is provided at a most downstream side of the refrigerant flow of the downstream flow passage portion vertically above a refrigerant suction port (12a) through which the refrigerant is drawn into the compressor.

4. The connection device according to any one of claims 1 to 3, wherein the downstream flow passage portion is arranged such that the most downstream side of the refrigerant flow of the downstream flow passage portion is vertically lower than the most upstream side of the refrigerant flow of the upstream flow passage portion.

5. The inner diameter of the upstream flow passage portion is formed to a size corresponding to a most downstream portion of the refrigerant flow of the inlet pipe to be connected, 5. The connection device according to claim 1, wherein the inner diameter of the downstream flow passage portion is larger than the inner diameter of the upstream flow passage portion and is formed to a size corresponding to the upstreammost portion of the refrigerant flow of the outflow pipe.

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