JP2022191811A - connection device - Google Patents

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

The present disclosure relates to connection devices.

2. Description of the Related Art Conventionally, there has been known a connecting device that connects a plurality of components that constitute a refrigerant circulation cycle in which a refrigerant circulates so as to communicate with each other (see, for example, Patent Literature 1).

Japanese Unexamined Patent Application Publication No. 2014-31998

The connection device described in Patent Literature 1 has a structure for communicating refrigerant pipes having a positional relationship in three directions. Specifically, the connection device described in Patent Document 1 is T-shaped, and joints to which refrigerant pipes are connected are provided at both ends, and refrigerant pipes are also provided at positions orthogonal to the joints at both ends. A connecting joint is provided.

In the connection device having such a configuration, for example, when the inflow pipe for inflow of the refrigerant is connected to the joints at both ends, and the outflow pipe for outflow of the refrigerant is connected to the remaining joints, the inflow from the joints at both ends As the refrigerants join and collide, the direction of flow of the refrigerant is bent by 90°. Such collisions of the coolant and changes in the flow direction of the coolant cause pressure loss, and are therefore desirably suppressed.

An object of the present disclosure is to provide a connection device capable of suppressing pressure loss.

The invention according to claim 1,
In a refrigeration cycle device (10) in which a refrigerant circulates, at least one inflow pipe (11a, 11b, 11d, 11e) and at least one outflow pipe (11c) are connected, and the refrigerant flowing from the inflow pipe flows through the inflow pipe. A connection device that leads to an outflow pipe provided on the downstream side of the refrigerant flow,
a housing (110, 210, 310);
upstream flow path portions (120, 130, 220, 230, 240, 320, 330, 510) that are connected one-to-one to the inflow pipe and allow the refrigerant to flow into the interior of the housing;
The downstream flow passages (140, 250, 140, 250, 350, 520, 530) and
merging portions (141, 142, 251, 252, 351) for joining the refrigerant flowing from the plurality of upstream flow passages to the downstream flow passages; Either one of the branches (540) that branches into
When the confluence portion is provided, when the direction in which the downstream flow path portion extends from the confluence portion toward the downstream side of the refrigerant flow in the downstream flow path portion is defined as the downstream direction, at least one of the plurality of upstream flow path portions is: extends at an angle greater than 0° and less than 90° with respect to the downstream direction,
When the branched portion is provided, when the direction in which the upstream channel portion extends from the branched portion toward the upstream side of the refrigerant flow of the upstream channel portion is defined as the upstream direction, at least one of the plurality of downstream channel portions is: It extends at an angle greater than 0° and less than 90° with respect to the upstream direction.

According to this, when the connection device is configured to merge the refrigerant inside, compared to the configuration in which the upstream flow path portion extends with a deviation of 90° from the predetermined confluence reference direction, the upstream flow path portion It is possible to suppress the pressure loss when the flow direction of the refrigerant changes when joining the downstream flow path portion from the .

On the other hand, when the connection device is configured to branch the refrigerant inside, compared to the configuration in which the downstream channel portion extends with a deviation of 90° from the predetermined branch reference direction, the upstream channel portion It is possible to suppress the pressure loss when the flow direction of the refrigerant changes when the refrigerant that has flowed from is branched.

It should be noted that the reference numerals in parentheses attached to each component etc. indicate an example of the correspondence relationship between the component etc. and specific components etc. described in the embodiments described later.

1 is a schematic configuration diagram of a vehicle air conditioner according to a first embodiment; FIG. It is a block diagram showing a control device of a vehicle air conditioner concerning a 1st embodiment. 1 is a perspective view of a connection device according to a first embodiment; FIG. FIG. 4 is a sectional view along IV-IV in FIG. 3; It is a figure which shows the positional relationship of the connection device which concerns on 1st Embodiment, and a compressor. FIG. 5 is a relational diagram showing the relationship between the pressure loss of the connection device, the manufacturing cost of the connection device, and the diameter ratio of the connection portion according to the first embodiment. FIG. 4 is a diagram showing the flow direction of the coolant when the coolant flows in from the steep upstream channel portion of the connection device according to the first embodiment; FIG. 5 is a diagram showing the direction of flow of the coolant when the coolant flows in from the low upstream channel portion of the connection device according to the first embodiment; FIG. 4 is a diagram showing the flow direction of the coolant when the coolant flows from the steep upstream channel portion and the low upstream channel portion of the connection device according to the first embodiment; FIG. 4 is a perspective view of a first comparative connection device; FIG. 11 is a perspective view of a second comparative connecting device; It is a perspective view of the connection device which concerns on 2nd Embodiment. 13 is a cross-sectional view taken along line XIII-XIII of FIG. 12; FIG. FIG. 10 is a diagram showing the flow direction of a coolant flowing inside the housing of the connection device according to the second embodiment; It is a schematic block diagram of the vehicle air conditioner which concerns on 3rd Embodiment. It is a perspective view of the connection device which concerns on 3rd Embodiment. FIG. 17 is a cross-sectional view taken along line XVII-XVII of FIG. 16; FIG. 11 is a diagram showing the flow direction of a coolant flowing inside the housing of the connection device according to the third embodiment; FIG. 11 is a cross-sectional view of a connection device according to a third modified example of the third embodiment; FIG. 11 is a cross-sectional view of a connecting device according to a fourth modified example of the third embodiment; It is a perspective view of the connection device which concerns on 4th Embodiment. It is a sectional view of the connecting device concerning other embodiments.

Hereinafter, embodiments of the present disclosure will be described with reference to the drawings. In the following embodiments, the same or equivalent parts as those described in the preceding embodiments are denoted by the same reference numerals, and description thereof may be omitted. Moreover, when only some of the components are described in the embodiments, the components described in the preceding embodiments can be applied to the other parts of the components. The following embodiments can be partially combined with each other, even if not explicitly stated, as long as there is no problem with the combination.

(First embodiment)
This embodiment will be described with reference to FIGS. 1 to 11. FIG. 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 running from a motor generator 62, which will be described later. The vehicle air conditioner 1 not only heats and cools air blown into the vehicle interior, 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 or the like. Therefore, an object to be cooled that is different from the blown air in the refrigeration cycle apparatus 10 of this embodiment is the battery 60 .

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 indoor air conditioning unit 50, and the like.

The refrigeration cycle device 10 is configured to be switchable to refrigerant circuits for various operation modes in order to air-condition the interior of the vehicle. Specifically, the refrigerating cycle device 10 is configured such that the refrigerant circuit can be switched to a cooling mode refrigerant circuit, a dehumidifying/heating mode refrigerant circuit, a heating mode refrigerant circuit, or the like, as a refrigerant circuit in an operation mode for air conditioning. . 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 operation mode for air conditioning. Furthermore, the refrigerating cycle device 10 is configured to be switchable to a cooling mode refrigerant circuit that cools the battery 60 without performing air conditioning.

In addition, the refrigerating cycle device 10 employs an HFO-based refrigerant (specifically, R1234yf) as a refrigerant, and is a vapor compression type in which the pressure of the discharged refrigerant discharged from the compressor 12 does not exceed the critical pressure of the refrigerant. It constitutes a subcritical refrigeration cycle. The refrigerating cycle device 10 is a heat pump cycle.

Furthermore, the refrigerant is mixed with oil for lubricating the compressor 12 (that is, refrigerating machine oil). For the oil, for example, polyalkylene glycol oil (that is, PAG oil) having compatibility with the liquid refrigerant is adopted. A portion of the oil circulates in the cycle together with the refrigerant.

As shown in FIG. 1, the refrigeration cycle device 10 has a refrigerant circulation passage 11 for flowing refrigerant. The refrigerant circulation passage 11 includes a compressor 12 that compresses the refrigerant, a water-refrigerant heat exchanger 13 that exchanges heat between the refrigerant and the heat medium, an indoor evaporator 14, a chiller 16, and a refrigerant pressure. An evaporation pressure regulating valve 15, a first expansion valve 17a, and a second expansion valve 17b to be controlled are provided. In addition, the refrigerant circulation passage 11 is provided with a refrigerant branching portion 18 for branching the flow of 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 it to the downstream refrigerant passage. there is Further, in the refrigerant circulation passage 11, first refrigerant temperature sensors 19a to third refrigerant temperature sensors 19a to 19c for detecting the temperature of the refrigerant flowing through the refrigerant circulation passage 11, A refrigerant pressure sensor 19d to a third refrigerant pressure sensor 19f are provided.

The compressor 12 takes in the refrigerant in the refrigeration cycle device 10, compresses it, and discharges it. The compressor 12 is arranged in a drive device room that is arranged in front of the vehicle compartment and houses an electric motor and the like. The driving device room forms a space in which at least a portion of equipment (for example, a motor generator 62 to be described later) used for generating or adjusting the driving force for running the vehicle is arranged.

The compressor 12 is an electric compressor in which a fixed displacement type compression mechanism with a fixed discharge displacement is rotationally driven by an electric motor. Compressor 12 has its rotation speed (that is, refrigerant discharge capacity) controlled by a control signal output from control device 70, which will be described later. The inlet side of the refrigerant passage of the water-refrigerant heat exchanger 13 is connected to the discharge port of the compressor 12 .

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

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

The water-refrigerant heat exchanger 13 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, thereby heating the high-temperature side heat medium. Exchanger. 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. Therefore, the refrigerant passage of the water-refrigerant heat exchanger 13 is provided with a condensing portion 13a, a receiver portion 13b, and a supercooling portion 13c.

The condensing section 13a is a condensing heat exchange section 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 condense the high-pressure refrigerant. The receiver portion 13b is a liquid receiving portion that separates the gas-liquid refrigerant that has flowed out of the condensation portion 13a and stores the separated liquid-phase refrigerant. The supercooling part 13c is a heat exchange part for supercooling that causes heat exchange between the liquid-phase refrigerant flowing out of the receiver part 13b and the high-temperature side heat medium to supercool the liquid-phase refrigerant. In addition, the inlet side of a refrigerant branch portion 18 having three inlets and outlets communicating with each other is connected to the outlet of the refrigerant passage of the water-refrigerant heat exchanger 13 .

The refrigerant branch portion 18 is a three-way joint portion that has one inlet and two outlets and causes the refrigerant that has flowed in from one inlet to flow out to one outlet and the other outlet. The refrigerant branch portion 18 may be formed by connecting a plurality of pipes or by providing a plurality of refrigerant passages in a metal block or a resin block.

One outflow port of the refrigerant branch portion 18 is connected to the inlet side of the first expansion valve 17a. The other outflow port of the refrigerant branch portion 18 is connected to the inlet side of the second expansion valve 17b.

The first expansion valve 17a reduces the pressure of the high-pressure refrigerant flowing out of the refrigerant passage of the water-refrigerant heat exchanger 13 at least during the operation mode in which the vehicle interior is cooled, and the flow rate of the refrigerant flowing out downstream (that is, the mass It is a cooling decompression unit that adjusts the flow rate). The first expansion valve 17a is an electric variable throttle mechanism that includes a valve body that can change the opening degree of the throttle and an electric actuator that changes the opening degree of the valve body.

The first expansion valve 17a of the present embodiment is configured such that the throttle opening can be changed in the range of 0 to 100% by adjusting the opening area of the valve body. That is, the first expansion valve 17a is fully opened (that is, the throttle opening is set to 100%) so that the first expansion valve 17a has a fully open function that functions simply as a refrigerant passage without exhibiting the flow rate adjustment action and the refrigerant pressure reduction action. have. Further, the first expansion valve 17a has a fully closing function of closing the refrigerant passage by fully closing the valve opening (that is, setting the throttle opening to 0%). The refrigerant inlet side of the indoor evaporator 14 is connected to the outlet of the first expansion valve 17a.

The second expansion valve 17b reduces the pressure of the refrigerant flowing out of the refrigerant passage of the water-refrigerant heat exchanger 13 and adjusts the flow rate of the refrigerant flowing out to the downstream side at least in the operation mode for heating the vehicle interior. This is the decompression section. The second expansion valve 17b has the same basic configuration as the first expansion valve 17a. The inlet side of the refrigerant passage of the chiller 16 is connected to the outlet of the second expansion valve 17b.

And the 1st expansion valve 17a and the 2nd expansion valve 17b can switch the refrigerant circuit of each operation mode by this full-open function and full-close function. Therefore, the first expansion valve 17a and the second expansion valve 17b also function as refrigerant circuit switching units. The operations of the first expansion valve 17a and the second expansion valve 17b are controlled by control signals (that is, control pulses) output from the control device 70 .

The indoor evaporator 14 evaporates the low-pressure refrigerant by exchanging heat between the low-pressure refrigerant decompressed by the first expansion valve 17a and air blown from a blower 53, which will be described later, and causes the low-pressure refrigerant to exhibit heat absorption. It is a cooling heat exchanger that cools the blown air. The indoor evaporator 14 is arranged in an air conditioning case 51 of an indoor air conditioning unit 50, which will be described later. An air-conditioning inflow pipe 11 a that guides the refrigerant flowing out of the indoor evaporator 14 to the connection device 100 is connected to the refrigerant outlet of the indoor evaporator 14 . In this embodiment, the indoor evaporator 14 functions as an air conditioning heat exchanger.

The air conditioning inflow pipe 11a forms a refrigerant passage through which refrigerant flows, and is connected to the indoor evaporator 14 on the upstream side of the refrigerant flow and to the connection device 100 on the downstream side of the refrigerant flow. The air-conditioning inflow pipe 11 a is an inflow pipe that allows refrigerant to flow into the connection device 100 .

The air-conditioning inflow pipe 11a is sized to be inserted into the refrigerant outlet of the indoor evaporator 14 and the refrigerant inlet of the connecting device 100 . Specifically, in this embodiment, a refrigerant pipe having an outer diameter of 15.88 mm from the inlet side to the outlet side is adopted as the air conditioning inflow pipe 11a. On the other hand, the inner diameter of the refrigerant outlet of the indoor evaporator 14 and the inner diameter of the later-described rapid flow inlet 121 through which the refrigerant flows into the connecting device 100 are slightly larger than 15.88 mm.

Note that the air conditioning inflow pipe 11a may employ a refrigerant pipe having an outer diameter different from 15.88 mm from the inlet side to the outlet side. In this case, the refrigeration cycle device 10 attaches to the indoor evaporator 14 and the connection device 100 a refrigerant pipe conversion member having an inlet side outer diameter and an outlet side outer diameter that are different in size, and the indoor evaporator 14 and The connection device 100 may be configured to connect the air conditioning inflow pipe 11a.

Further, a second refrigerant temperature sensor 19b for detecting the temperature of the refrigerant discharged from the indoor evaporator 14 and a second refrigerant pressure sensor 19e for detecting the pressure of the refrigerant discharged from the indoor evaporator 14 are connected to the air conditioning inflow pipe 11a. is provided. Furthermore, the air conditioning inflow pipe 11a is provided with an evaporation pressure regulating valve 15 for regulating the pressure of the refrigerant discharged from the indoor evaporator 14. As shown in FIG.

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

The evaporating pressure regulating valve 15 functions to maintain the refrigerant evaporating 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 evaporating pressure regulating valve 15 is composed of a mechanical variable throttling mechanism that increases the degree of opening of the valve as the pressure of the refrigerant on the outlet side of the indoor evaporator 14 increases. Thereby, the evaporating pressure regulating valve 15 maintains the temperature at which the refrigerant evaporates in the indoor evaporator 14 at or above the frost suppression temperature (for example, 1° C.) that can suppress frost formation on the indoor evaporator 14 .

The chiller 16 is an evaporating section that exchanges heat between the low-pressure refrigerant decompressed by the second expansion valve 17b and the low-temperature side heat medium circulating in the low-temperature side heat medium circuit 40, thereby evaporating the low-pressure refrigerant and exhibiting heat absorption. be. The chiller 16 has a refrigerant passage through which the low-pressure refrigerant discharged 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. A cooling part inflow pipe 11 b for guiding the refrigerant flowing out of the chiller 16 to the connecting device 100 is inserted into the outlet of the refrigerant passage of the chiller 16 .

The cooling section inflow pipe 11b forms a refrigerant passage through which refrigerant flows, and is connected to the chiller 16 on the upstream side of the refrigerant flow and to the connection device 100 on the downstream side of the refrigerant flow. The cooling unit inflow pipe 11 b is an inflow pipe that allows the refrigerant to flow into the connecting device 100 .

The cooling section inflow pipe 11 b is sized to be inserted into the refrigerant passage outlet of the chiller 16 and the refrigerant inlet of the connecting device 100 . Specifically, in the present embodiment, a refrigerant pipe having an outer diameter of 15.88 mm from the inlet side to the outlet side is adopted as the cooling section inflow pipe 11b. On the other hand, the inner diameter of the outlet of the refrigerant passage of the chiller 16 and the inner diameter of the later-described low inlet 131 through which the refrigerant flows into the connecting device 100 are slightly larger than 15.88 mm. The outer diameter of the cooling section inflow pipe 11b is the same as that of the air conditioning inflow pipe 11a.

In addition, as the cooling section inflow pipe 11b, a refrigerant pipe having an outer diameter different from 15.88 mm from the inlet side to the outlet side may be adopted. In this case, the refrigeration cycle device 10 attaches to the chiller 16 and the connection device 100 a refrigerant pipe conversion member having an inlet side outer diameter and an outlet side outer diameter that are different in size, and the chiller 16 and the connection device 100 A configuration in which the cooling unit inflow pipe 11b is connected may be used. Further, a refrigerant pipe having an outer diameter different from that of the air conditioning inflow pipe 11a may be employed for the cooling portion inflow pipe 11b.

A third refrigerant temperature sensor 19c for detecting the temperature of the refrigerant flowing out from the refrigerant passage of the chiller 16 and a third refrigerant pressure sensor for detecting the pressure of the refrigerant flowing out from the refrigerant passage of the chiller 16 are provided in the cooling unit inflow pipe 11b. 19f is provided.

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

The connection device 100 merges the refrigerant flowing from the air conditioning inflow pipe 11a and the cooling part inflow pipe 11b and guides it to the compressor outflow pipe 11c provided downstream of the air conditioning inflow pipe 11a and the cooling part inflow pipe 11b. It is a refrigerant pipe connection member. The connecting device 100 has a rapid inlet 121 through which the refrigerant flows into the connecting device 100, a low inlet 131, and a refrigerant outlet 143 through which the refrigerant flowing into the connecting device 100 flows out.

The connecting device 100 has a rapid inlet 121 to which the air conditioner inlet pipe 11a is connected, a low inlet 131 to which the cooling section inlet pipe 11b is connected, and a refrigerant outlet 143 to which the compressor outlet pipe 11c is connected. Details of the connection device 100 will be described later.

The compressor outflow pipe 11c forms a refrigerant passage through which refrigerant flows, and is connected to the connecting device 100 on the upstream side of the refrigerant flow and to the compressor 12 on the downstream side of the refrigerant flow. The compressor outflow pipe 11 c is an outflow pipe that guides the refrigerant that has flowed out of the connection device 100 to the compressor 12 .

Compressor outflow pipe 11 c is sized to be inserted into refrigerant suction port 12 a of compressor 12 and refrigerant outflow port 143 of connecting device 100 . Specifically, in this embodiment, a refrigerant pipe having an outer diameter of 19.05 mm from the inlet side to the outlet side is adopted as the compressor outflow pipe 11c. On the other hand, 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 connecting device 100 are slightly larger than 19.05 mm. The outer diameter of the compressor outflow pipe 11c is larger than the outer diameters of the air conditioning inflow pipe 11a and the cooling part inflow pipe 11b.

As the compressor outflow pipe 11c, a refrigerant pipe having an outer diameter different from 19.05 mm from the inlet side to the outlet side may be adopted. In this case, the refrigerating cycle device 10 attaches to the connection device 100 and the compressor 12 a refrigerant pipe conversion member having an inlet side outer diameter and an outlet side outer diameter that are different in size, so that the connection device 100 and the compressor 12 may be connected to the compressor outflow pipe 11c. Further, the compressor outflow pipe 11c may employ a refrigerant pipe having the same outer diameter as the air conditioning inflow pipe 11a and the cooling part inflow pipe 11b, or a refrigerant pipe having a smaller outer diameter than the air conditioning inflow pipe 11a and the cooling part inflow pipe 11b. .

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. Ethylene glycol, dimethylpolysiloxane, a solution containing a nanofluid or the like, an antifreeze liquid, or the like can be used as the high-temperature side heat medium. 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 control valve 33, a high temperature side radiator 34, a heater core 35, and a high temperature side heat medium. A junction 36 is arranged. Further, in the high temperature side heat medium circuit 30, a first high temperature side heat medium temperature sensor 37a and a second high temperature side heat medium temperature sensor 37b for detecting the temperature of the high temperature side heat medium flowing through the high temperature side heat medium circuit 30 are arranged. It is

The high temperature side heat medium pump 31 is a water pump that pressure-feeds 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 rotational speed (that is, pumping capacity) is controlled by a control voltage output from the control device 70 .

An electric heater 32 is connected to the outlet of the water passage of the water-refrigerant heat exchanger 13 . In addition, in the refrigerant passage on the outlet side of the water passage of the water-refrigerant heat exchanger 13, a first high temperature side for detecting 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 A heat medium temperature sensor 37a is provided. 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 .

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 . A PTC heater having a PTC element (that is, a positive temperature coefficient thermistor) is employed as the electric heater 32 in the high temperature side heat medium circuit 30 . 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 a high temperature side flow control valve 33 having three inlets and outlets that can communicate with each other.

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

The high temperature side flow control valve 33 adjusts the high temperature side flow ratio by adjusting the rotational position of the valve body. Further, the high-temperature-side flow control valve 33 adjusts the rotational position of the valve body so that the high-temperature-side heat medium that has flowed into the high-temperature-side flow control valve 33 is directed to only one of the high-temperature side radiator 34 and the heater core 35 . It can also be drained to

The high temperature side flow control valve 33 can change the mode of use of the high temperature side heat medium by adjusting the high temperature side flow rate ratio. The high-temperature-side heat medium circuit 30 increases the flow rate of the high-temperature-side heat medium flowing into the heater core 35 by means of the high-temperature-side flow control valve 33, for example, so that the heat of the high-temperature-side heat medium is used to heat the blast air, thereby operating the vehicle. You can heat the room. On the other hand, the high temperature side heat medium circuit 30 increases the flow rate of the high temperature side heat medium flowing into the high temperature side radiator 34 by means of the high temperature side flow control valve 33, for example, so that the heat of the high temperature side heat medium is transferred to the outside air. can be released. The operation of the high temperature side flow control valve 33 is controlled by a control signal output from the control device 70 .

One outflow port of the high temperature side flow control valve 33 is connected to the heat medium inlet side of the high temperature side radiator 34 . The heat medium inlet side of the heater core 35 is connected to the other outflow port of the high temperature side flow control valve 33 . A second high-temperature-side heat medium temperature sensor 37b for detecting the temperature of the high-temperature-side heat medium before flowing into the heater core 35 is provided in the refrigerant passage on the other outlet side of the high-temperature-side flow control valve 33. . The second high-temperature-side heat medium temperature sensor 37 b sends a detection signal to the control device 70 according to the temperature of the high-temperature-side heat medium that has flowed out of the high-temperature-side flow rate control valve 33 and before flowing into the heater core 35 .

The high temperature side radiator 34 is a high temperature side outside air heat exchange section that exchanges heat between the high temperature side heat medium heated in the water-refrigerant heat exchanger 13 and outside air blown from an outside air fan (not shown). The high temperature side radiator 34 is arranged on the front side in the driving device room. A heat medium outlet of the high temperature side radiator 34 is connected to one inlet side of the high temperature side heat medium junction 36 .

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

The high-temperature-side heat medium confluence portion 36 is a three-way joint portion that has two inlets and one outlet, and joins the refrigerant that has flowed in from the two inlets and flows out to one outlet. The inlet side of the high temperature side heat medium pump 31 is connected to the outlet of the high temperature side heat medium junction 36 . The high-temperature-side heat medium junction section 36 guides the high-temperature-side heat medium flowing from the high-temperature-side radiator 34 and the heater core 35 to the high-temperature-side heat-medium pump 31 .

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 to reduce the high temperature in the heater core 35 . Adjust the amount of heat released from the side heating medium to the blast air. That is, the high temperature side heat medium circuit 30 can adjust the heating amount of the blown air in the heater core 35 .

That is, in the present embodiment, the components of the water-refrigerant heat exchanger 13 and the high-temperature side heat medium circuit 30 constitute a heating unit that heats the blown air using the refrigerant discharged from the compressor 12 as a heat source. there is

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 adopted. 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 electric device passage 44 are arranged in the low temperature side heat medium circuit 40. . In addition, the low temperature side heat medium circuit 40 includes a first low temperature side heat medium junction 45a and a second low temperature side heat medium junction 45b for joining the low temperature side heat medium flowing from the plurality of refrigerant passages, and a plurality of refrigerant flow paths. A low-temperature side heat medium branch portion 46 that branches to the refrigerant passage is provided. Furthermore, the low-temperature side heat medium circuit 40 is provided with 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. ing.

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 the same as 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 battery side three-way valve 42 is connected to the outlet of the water passage of the chiller 16 .

The battery side three-way valve 42 has one inflow port and two outflow ports, and the flow rate of the low temperature side heat medium flowing into the cooling water passage of the battery 60 with respect to the flow rate of the low temperature side heat medium flowing into the low temperature side radiator 43 is determined. It is a low temperature side flow ratio adjustment unit that adjusts the low temperature side flow ratio. 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 the first low temperature side heat medium junction 45a, and the other outlet is connected to the cooling water passage of the battery 60. connected to the inlet side. The battery-side three-way valve 42 and the device-side three-way valve 44 c described later have the same basic configuration as the high-temperature side flow control valve 33 .

The battery side three-way valve 42 adjusts the low temperature side flow rate ratio by adjusting the rotational position of the valve body. Moreover, the battery-side three-way valve 42 can also allow the low-temperature-side heat medium that has flowed thereinto to flow out only to either the low-temperature-side radiator 43 or the cooling water passage of the battery 60 .

For example, the battery-side three-way valve 42 fully closes one outflow port and opens the other outflow port, so that the entire flow rate of the low temperature side heat medium flowing out of the water passage outlet of the chiller 16 is It passes through the cooling water passage and returns 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, so that the total flow rate of the low temperature side heat medium flowing out from the outlet of the water passage of the chiller 16 is It passes through the low temperature side radiator 43 and returns to the suction side of the device pump 44b. The operation of the battery-side three-way valve 42 is controlled by a control signal output from the control device 70 .

A first low-temperature-side heat medium temperature sensor 47a for detecting the temperature of the low-temperature-side heat medium before flowing into the cooling water passage of the battery 60 is provided in the refrigerant passage on the other outlet side of the battery-side three-way valve 42. It is The first low-temperature-side heat medium temperature sensor 47 a transmits a detection signal to the control device 70 according to the temperature of the low-temperature-side heat medium before flowing out from the outlet of the water passage of the chiller 16 and flowing into the cooling water passage of the battery 60 . do.

The first low temperature side heat medium junction 45 a is a three-way joint having the same basic configuration as the high temperature side heat medium junction 36 . One inlet of the first low temperature side heat medium junction 45a is connected to one outlet side of the battery side three-way valve 42, and the other inlet is connected to the refrigerant flow downstream side of the electric device passage 44. In addition, the heat medium inlet side of the low temperature side radiator 43 is connected to the outflow port. The first low-temperature side heat medium junction 45 a guides the refrigerant flowing from the battery-side three-way valve 42 and the electric device passage 44 to the low-temperature side radiator 43 .

The low-temperature-side radiator 43 is a low-temperature-side outside air heat exchange section that exchanges heat between the low-temperature-side heat medium flowing out of the battery-side three-way valve 42 and outside air blown from an outside air fan (not shown). The low temperature side radiator 43 is arranged on the front side in the driving device room and downstream of the high temperature side radiator 34 in the flow of outside air.

Therefore, the low-temperature side radiator 43 exchanges heat between the outside air after passing through the high-temperature side radiator 34 and the low-temperature side heat medium. The low temperature side radiator 43 may be formed integrally with the high temperature side radiator 34 . A heat medium outlet of the low temperature radiator 43 is connected to one inlet side of the second low temperature side heat medium junction 45 b via a low temperature side heat medium branch 46 .

A second low-temperature-side heat medium temperature sensor 47 b that detects the temperature of the low-temperature-side heat medium flowing out of the low-temperature-side radiator 43 is provided in the refrigerant passage on the heat-medium outlet side of the low-temperature-side radiator 43 . The second low-temperature-side heat medium temperature sensor 47 b transmits a detection signal corresponding to the temperature of the low-temperature-side heat medium flowing out of the low-temperature-side radiator 43 to the control device 70 . The second low-temperature-side heat medium temperature sensor 47b is provided to determine whether or not the low-temperature-side radiator 43 is frosted based on the temperature of the low-temperature-side heat medium flowing out from the low-temperature-side radiator 43 .

The low-temperature side heat medium branch portion 46 is a three-way joint portion that has one inlet and two outlets, and branches the refrigerant that has flowed in from the inlet and flows out from one outlet and the other outlet. . One outflow port of the low temperature side heat medium branching portion 46 is connected to one inflow port side of the second low temperature side heat medium junction portion 45b, and the other outflow port is connected to the refrigerant flow upstream side of the electric device passage 44. It is The low temperature side heat medium branching portion 46 guides the refrigerant flowing from the low temperature side radiator 43 to the second low temperature side heat medium junction portion 45 b and the electric device passage 44 .

One inlet of the second low-temperature-side heat medium junction 45b is connected to one outlet of the low-temperature-side heat medium branch 46, and the other inlet is connected to the outlet of the cooling water passage of the battery 60. In addition, the suction port side of the low temperature side heat medium pump 41 is connected to the outflow port. The second low temperature side heat medium junction 45 b guides the refrigerant flowing from the cooling water passages of the low temperature side radiator 43 and the battery 60 to the low temperature side heat medium pump 41 .

Battery 60 stores power to be supplied to a plurality of electrical devices. The battery 60 is an assembled battery formed by electrically connecting a plurality of battery cells (not shown) in series or in parallel. The battery cells are rechargeable secondary batteries (lithium ion batteries in this embodiment). The battery 60 has a plurality of battery cells stacked in a substantially rectangular parallelepiped shape and housed in a dedicated case.

This type of secondary battery generates heat during operation (that is, during charging and discharging). Secondary batteries tend to deteriorate at high temperatures. Furthermore, when the temperature of the secondary battery becomes low, the chemical reaction does not progress easily, and the output tends to decrease. Therefore, the temperature of the secondary battery should be maintained within an appropriate temperature range (for example, 15° C. or higher and 55° C. or lower) where the charge/discharge capacity of the secondary battery can be fully utilized. desirable.

Therefore, in the present embodiment, a cooling water passage for circulating the low-temperature side heat medium is formed inside the exclusive case of the battery 60 . The passage configuration of the cooling water passage is a passage configuration in which a plurality of passages are connected in parallel inside the dedicated case. Thereby, the cooling water passage is formed so that the temperature of all the battery cells can be adjusted equally. Therefore, the battery 60 of this embodiment is an 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.

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 cooling water passage of the battery 60, so that the low temperature side heat medium is The amount of heat absorbed from the battery 60 can be adjusted. That is, in the present embodiment, the components of the chiller 16 and the low-temperature side heat medium circuit 40 constitute a cooling unit that cools the battery 60 by evaporating the refrigerant flowing out of the second expansion valve 17b.

Further, an electric device passage 44 is connected to the low temperature side heat medium circuit 40 of the present embodiment. The electric device passage 44 is a heat medium passage that returns the refrigerant that has flowed 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 again, and one side of the electric device passage 44 is a low temperature side heat medium branch portion 46 . , and the other side is connected to the first low temperature side heat medium junction 45a. The electrical device passage 44 includes a device passage junction 44a, a device 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, a device side three-way valve 44c, and the like. are placed.

The device passage junction 44a is a three-way joint having the same basic configuration as the first low temperature side heat medium junction 45a and the second low temperature side heat medium junction 45b. One inlet of the device passage merging portion 44a is connected to the other outlet of the low temperature side heat medium branch portion 46, and the other inlet is connected to a bypass passage 44d that bypasses the low temperature side radiator 43. side is connected. Further, the suction port side of the equipment pump 44b is connected to the outflow port of the equipment passage merging portion 44a. The device passage joining portion 44a guides the refrigerant flowing from the low temperature side heat medium branch portion 46 and the bypass passage 44d to the device pump 44b.

The equipment pump 44 b is a water pump that pumps at least part of the low temperature side heat medium flowing out of the low temperature side radiator 43 to the 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 .

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

Inverter 61 generates heat during operation. When the temperature of the inverter 61 becomes high, deterioration of the electric circuit tends to progress. Therefore, the temperature of the inverter 61 needs to be maintained at a temperature lower than the reference heat-resistant temperature (for example, 130° C. or lower) at which the electric circuit can be protected.

Therefore, in the present embodiment, a cooling water passage for circulating the low-temperature side heat medium is formed in the housing portion forming the outer shell of the inverter 61 . A cooling water passage of the inverter 61 is a heat exchange portion that exchanges heat between the low temperature side heat medium and the inverter 61 . The inlet side of the cooling water passage of the motor generator 62 is connected to the outlet of the cooling water passage of the inverter 61 .

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

Motor generator 62 generates heat during operation. When the temperature of the motor generator 62 becomes high, deterioration of the electric circuit tends to progress. Furthermore, when the temperature of the motor generator 62 becomes low, the sliding resistance increases and it becomes difficult to output a smooth rotational driving force. Therefore, the temperature of the motor generator 62 is maintained within an appropriate temperature range (for example, 80° C. or higher and 130° C. or lower) that can protect the electric circuit and smoothly output the rotational driving force. There is a need.

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

Transaxle device 63 is one of a plurality of electrical devices indirectly connected to battery 60 . The transaxle device 63 is a device in which a transmission and a final gear/differential gear are integrated.

The transaxle device 63 generates heat during operation. When the temperature of the transaxle device 63 becomes high, deterioration of the electric circuit tends to progress. Furthermore, when the temperature of the transaxle device 63 becomes low, it becomes difficult for the oil for lubricating the transaxle device 63 to circulate. Therefore, the temperature of the transaxle device 63 must be maintained within an appropriate temperature range (for example, -10°C or higher and 60°C or lower) to protect the electric circuit and ensure smooth oil circulation. There is

Therefore, in the present embodiment, a cooling water passage through which the low-temperature side heat medium flows is formed in the housing portion forming the outer shell of the transaxle device 63 . A cooling water passage of the transaxle device 63 is a heat exchange portion that exchanges heat between the low temperature side heat medium and the transaxle device 63 . The outlet of the cooling water passage of the transaxle device 63 is connected to the inlet side of the device-side three-way valve 44c.

A third low-temperature-side heat medium temperature sensor 47c for detecting the temperature of the low-temperature-side heat medium flowing out of the transaxle device 63 is provided in the coolant passage on the outlet side of the cooling water passage of the transaxle device 63 . The third low-temperature-side heat medium temperature sensor 47 c transmits a detection signal corresponding to the temperature of the low-temperature-side heat medium flowing out of the transaxle device 63 to the control device 70 .

The device-side three-way valve 44c has one inlet and two outlets, and the low-temperature side flow rate is the flow rate of the low-temperature side heat medium flowing into the bypass passage 44d with respect to the flow rate of the low-temperature side heat medium flowing into the low-temperature side radiator 43. It is a low temperature side flow rate ratio adjustment unit that adjusts the ratio. One outflow port of the device side three-way valve 44c is connected to the other inflow port of the first low-temperature side heat medium junction 45a, and the other outflow port is connected to the refrigerant flow upstream side of the bypass passage 44d.

The device side three-way valve 44c adjusts the rotational position of the valve body to adjust 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. adjust. In addition, the device-side three-way valve 44c can also allow the low-temperature-side heat medium that has flowed thereinto to flow out to only one of the low-temperature-side radiator 43 and the bypass passage 44d.

The device-side three-way valve 44 c fully closes one outflow port and opens the other outflow port, so that the entire flow rate of the low-temperature side heat medium flowing out of the cooling water passage of the transaxle device 63 is transferred to the low-temperature side radiator 43 . is bypassed and returned to the suction side of the device pump 44b. On the other hand, the device-side three-way valve 44c opens one outlet and fully closes the other outlet, thereby reducing the total flow rate of the low temperature side heat medium flowing out of the cooling water passage of the transaxle device 63. , the low-temperature side radiator 43, and returns to the suction side of the equipment pump 44b. The operation of the device-side three-way valve 44 c is controlled by a control signal output from the control device 70 .

Thus, 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 .

Next, the indoor air conditioning unit 50 will be described. The indoor air-conditioning unit 50 is for blowing into the passenger compartment the blown air whose temperature has been adjusted by the refrigeration cycle device 10 . The interior air-conditioning unit 50 is arranged inside the instrument panel (that is, the instrument panel) at the forefront of the vehicle interior.

As shown in FIG. 1, the indoor air conditioning unit 50 has an inside/outside air switching device 52, a blower 53, an indoor evaporator 14, a heater core 35, and an evaporator in an air passage formed in an air conditioning case 51 forming the outer shell. It accommodates a temperature sensor 54, an air mix door 56, and the like.

The air-conditioning case 51 forms an air passage for air blown into the vehicle interior. The air-conditioning case 51 has a certain degree of elasticity and is molded from a resin (for example, polypropylene) having excellent strength.

An inside/outside air switching device 52 is arranged on the most upstream side of the blowing 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 (that is, vehicle interior air) and outside air (that is, vehicle exterior air).

The inside/outside air switching device 52 continuously adjusts the opening areas of an inside air introduction port 52a for introducing inside air into the air conditioning case 51 and an outside air introduction port 52b for introducing outside air by an inside/outside air switching door 52c to introduce inside air. This is to change the introduction ratio between the air volume and the intake air volume of outside air. 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 arranged downstream of the inside/outside air switching device 52 in the blown air flow.

The blower 53 blows the air sucked through the inside/outside air switching device 52 into the vehicle interior. The blower 53 is an electric blower that drives a centrifugal multi-blade fan 53a with an electric motor 53b. The number of rotations (that is, the blowing capacity) of the blower 53 is controlled by the control voltage output from the control device 70 .

The indoor evaporator 14 and the heater core 35 are arranged in this order with respect to the blown air flow downstream of the blower 53 . In other words, the indoor evaporator 14 is arranged upstream of the heater core 35 in the air flow.

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

A cold air bypass passage 55 is provided in the air conditioning case 51 for bypassing the heater core 35 and allowing the blown air after passing through the indoor evaporator 14 to flow. An air mix door 56 is arranged downstream of the indoor evaporator 14 in the air conditioning case 51 and upstream of the heater core 35 .

The air mix door 56 adjusts the air volume ratio between the air volume of the air passing through the heater core 35 side and the air volume of the air passing through the cold air bypass passage 55 in the air after passing through the indoor evaporator 14. Department. 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 .

A mixing space 57 is arranged on the downstream side of the cold air bypass passage 55 in the air conditioning case 51 with respect to the blown air flow. The mixing space 57 is a space for mixing the blast air heated by the heater core 35 and the unheated blast air that has passed through the cold-air bypass passage 55 .

Furthermore, an opening hole for blowing out the blast air mixed in the mixing space 57 (that is, the conditioned air) into the vehicle interior, which is the space to be air-conditioned, is arranged at the downstream portion of the blast air flow of the air conditioning case 51 .

The openings include a face opening, a foot opening, and a defroster opening, all of which are not shown. The face opening hole is an opening hole for blowing the conditioned air toward the upper body of the passenger in the passenger compartment. The foot opening hole is an opening hole for blowing the conditioned air toward the passenger's feet. The defroster opening hole is an opening hole for blowing the conditioned air toward the inner surface of the vehicle front window glass.

These face opening hole, foot opening hole, and defroster opening hole are connected to the face air outlet, foot air outlet, and defroster air outlet (none of which are shown) provided in the passenger compartment via ducts forming air passages, respectively. It is connected.

Therefore, the temperature of the conditioned air mixed in the mixing space 57 is adjusted by the air mix door 56 adjusting the air volume ratio between the air volume passing through the heater core 35 and the air volume passing through the cold air bypass passage 55. Then, the temperature of the blown air (that is, the conditioned air) blown into the vehicle interior from each outlet is adjusted.

A face door, a foot door, and a defroster door (none of which are shown) are disposed upstream of the face opening, foot opening, and defroster opening, 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 froster opening hole.

These face door, foot door, and defroster door constitute an outlet mode switching device for switching outlet modes. These doors are connected to an electric actuator for driving the 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 .

The outlet mode switched by the outlet mode switching device specifically includes a face mode, a bi-level mode, a foot mode, and the like.

The face mode is an air outlet mode in which the face air outlet is fully opened and air is blown out from the face air outlet toward the upper body of the occupant in the passenger compartment. The bi-level mode is an outlet mode in which both the face outlet and the foot outlet are opened to blow air toward the upper body and feet of the occupants in the vehicle. The foot mode is an air outlet mode in which the foot air outlet is fully opened and the defroster air outlet is opened by a small degree of opening so that air is mainly blown out from the foot air outlet.

Furthermore, it is also possible to switch to the defroster mode by manually operating a blowout mode changeover switch provided on an operation panel 71, which will be described later, by the passenger. The defroster mode is an outlet mode in which the defroster outlet is fully opened and air is blown from the defroster outlet to the inner surface of the windshield.

Next, an outline of the control device 70 of this embodiment will be described with reference to FIG. 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 the air-conditioning control program stored in the ROM, and controls the operation of various controlled devices connected to the output side thereof. The ROM and RAM of the control device 70 are composed of non-transitional physical storage media.

2, the first refrigerant temperature sensor 19a to the third refrigerant temperature sensor 19c and the first refrigerant pressure sensor 19d to the third refrigerant pressure sensor 19f are connected to the input side of the control device 70. ing. Further, on the input side of the control device 70, the first high temperature side heat medium temperature sensor 37a, the second high temperature side heat medium temperature sensor 37b, the first low temperature side heat medium temperature sensor 47a to the third low temperature side heat medium temperature sensor 47a are provided. A sensor 47c and an evaporator temperature sensor 54 are connected. Furthermore, an inside air temperature sensor 72, an outside air temperature sensor 73, a solar radiation sensor 74, and the like are connected to the input side of the control device 70. FIG. Detection signals from these sensors are input to the controller 70 .

The inside air temperature sensor 72 is an inside air temperature detection unit that detects the temperature inside the vehicle (inside air temperature). The outside air temperature sensor 73 is an outside air temperature detection unit that detects the vehicle outside temperature (outside air temperature). The solar radiation sensor 74 is a solar radiation amount detection unit that detects the amount of solar radiation irradiated into the vehicle interior.

Further, the input side of the control device 70 is connected to an operation panel 71 arranged near the instrument panel in the front part of the passenger compartment, and operation signals from various operation switches provided on the operation panel 71 are input.

The various operation switches provided on the operation panel 71 include, specifically, an auto switch for setting or canceling the automatic control operation of the vehicle air conditioner 1, cooling of the air blown by the indoor evaporator 14, or air blowing by the heater core 35. There is an air conditioner switch that requests heating of the air. 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 the target temperature in the passenger compartment, and a blowout mode switch for manually setting the blowout mode.

Further, on the output side of the control device 70, as shown in FIG. A heater 32 is connected. An electric actuator for operating 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 device-side three-way valve 44c is connected to the output side of the control device 70. there is Furthermore, an inverter 61, a motor generator 62, a transaxle device 63, and the like are connected to the output side of the control device 70. FIG. The control device 70 of the present embodiment controls operations of various controlled devices connected to its output side.

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

These operation modes are switched by executing an air conditioning control program. The air-conditioning control program detects the inside temperature sensor 72, the outside temperature sensor 73, the solar radiation sensor 74, etc. when the auto switch of the operation panel 71 is turned on by the operation of the passenger and the automatic control of the vehicle interior is set. Executed by controller 70 based on the signal.

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

In the cooling mode, the controller 70 switches the refrigeration cycle device 10 to the cooling mode refrigerant circuit. Specifically, the control device 70 brings the first expansion valve 17a into the throttled state and brings the second expansion valve 17b into the fully closed state. Based on the detection signals transmitted from the second refrigerant temperature sensor 19b and the second refrigerant pressure sensor 19e, the controller 70 adjusts the degree of superheat of the refrigerant on the outlet side of the indoor evaporator 14 to a predetermined target degree of superheat. , determines the degree of opening of the first expansion valve 17a.

In addition, the control device 70 adjusts the rotational position of the valve body of the high temperature side flow rate adjustment valve 33 so that the high temperature side heat medium flowing into the high temperature side flow rate adjustment valve 33 does not flow out to the heater core 35 but flows out only to the high temperature side radiator 34 . to adjust. Further, the control device 70 adjusts the rotational position of the valve body of the device side three-way valve 44c so that the low temperature side heat medium flowing into the device side three way valve 44c does not flow out to the bypass passage 44d, but flows only to the low temperature side radiator 43. adjust. In addition, the control device 70 brings the battery-side three-way valve 42 into a fully closed state.

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

Therefore, in the refrigeration cycle device 10 in the cooling mode, the compressor 12→water-refrigerant heat exchanger 13→refrigerant branch portion 18→first expansion valve 17a→indoor evaporator 14→air conditioning inflow pipe 11a→connecting device 100→compressor The refrigerant circulates in the order of outflow pipe 11c→compressor 12 . Since the second expansion valve 17b is fully closed in the refrigeration cycle apparatus 10 in the cooling mode, the refrigerant does not flow into the cooling section inflow pipe 11b.

In the high-temperature side heat medium circuit 30 in the cooling mode, the high-temperature side heat medium flowing out of the water passage of the water-refrigerant heat exchanger 13 flows to the high-temperature side radiator 34 by the high-temperature side heat medium pump 31. Return to the suction port side of the pump 31 .

In the low-temperature side heat medium circuit 40 in the cooling mode, 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 device 63→the low-temperature side radiator 43→the equipment pump The low temperature side heat medium circulates in the order of 44b.

Thus, in the cooling mode, the refrigerant flowing out of the indoor evaporator 14 flows into the connecting device 100 from the rapid inlet 121 through the air conditioning inlet pipe 11a, but the refrigerant does not flow from the low inlet 131. Then, the connection device 100 causes the refrigerant that has flowed in from the rapid flow inlet 121 to flow out from the refrigerant outlet 143 and guides it to the compressor outflow pipe 11c.

Further, in the refrigeration cycle device 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 is a water-refrigerant heat exchanger. The refrigerant flowing out from 13 is decompressed. In the refrigeration cycle device 10, heat is absorbed from the air blown by the blower 53 in the indoor evaporator 14 to evaporate the refrigerant and cool the air.

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 by 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, respectively.

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 indoor evaporator 14 into the vehicle interior. 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 to operate the inverter 61, the motor generator 62, and the transaxle device 63. Allow to cool.

(2) Heating Mode The heating mode is an operation mode in which the vehicle interior is heated without cooling the battery 60 .

In the heating mode, the control device 70 switches the refrigeration cycle device 10 to the refrigerant circuit in the heating mode. Specifically, the control device 70 brings the first expansion valve 17a into the fully closed state and the second expansion valve 17b into the throttle state. The controller 70 adjusts the degree of supercooling of the refrigerant on the outlet side of the chiller 16 to a predetermined target degree of supercooling based on the detection signals transmitted from the third refrigerant temperature sensor 19c and the third refrigerant pressure sensor 19f. , determines the degree of opening of the second expansion valve 17b.

Further, the control device 70 adjusts the rotational position of the valve element of the high temperature side flow rate adjustment valve 33 so that the high temperature side heat medium flowing into the high temperature side flow rate adjustment valve 33 does not flow out to the high temperature side radiator 34 but flows out only to the heater core 35 . to adjust.

Furthermore, the control device 70 controls the valve body 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 out to the cooling water passage of the battery 60 but only flows out to the low temperature side radiator 43 . Adjust the rotation position. Then, the control device 70 adjusts the rotational position of the valve body of the device side three-way valve 44c so that the low temperature side heat medium flowing into the device side three way valve 44c does not flow out to the low temperature side radiator 43 but flows out only to the bypass passage 44d. adjust.

In addition, the control device 70 operates the electric actuator of the air mix door 56 so that the total amount of air that has passed through the indoor evaporator 14 passes through the heater core 35 . Further, the control device 70 controls the electric power supply based on the 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. The heating capacity of the heater 32 is adjusted as required.

Then, 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. Further, the control device 70 outputs a control signal to operate the high temperature side heat medium pump 31, the low temperature side heat medium pump 41, and the blower 53. FIG.

Therefore, in the refrigeration cycle device 10 in the heating mode, the compressor 12→water-refrigerant heat exchanger 13→refrigerant branch portion 18→second expansion valve 17b→chiller 16→cooling portion inflow pipe 11b→connection device 100→compressor outflow The refrigerant circulates in the order of piping 11c→compressor 12 . Since the first expansion valve 17a is fully closed in the refrigeration cycle apparatus 10 in the heating mode, the refrigerant does not flow into the air conditioning inflow pipe 11a.

In addition, in the high temperature side heat medium circuit 30 in the heating mode, the high temperature side heat medium flowing out of the water passage of the water-refrigerant heat exchanger 13 flows to the heater core 35 by the high temperature side heat medium pump 31, and the high temperature side heat medium pump 31 back to the inhaler.

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 into the low-temperature side radiator 43 and flow into the low-temperature side heat medium pump 41 suction port. back to Further, in the low-temperature side heat medium circuit 40 in the heating mode, 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 device 63→the bypass passage 44d→the equipment pump 44b. The low temperature side heat medium circulates in the order of .

Thus, in the heating mode, the refrigerant flowing out of the chiller 16 flows into the connection device 100 from the low inlet 131 through the cooling section inlet pipe 11b, but the refrigerant does not flow from the rapid inlet 121. 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 pipe 11c.

Further, in the refrigeration cycle device 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 is a water-refrigerant heat exchanger. The refrigerant flowing out from 13 is decompressed. In the refrigeration cycle device 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.

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 air blown from the blower 53 in the heater core 35, Heat the blast air.

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 . Then, the heated low temperature side heat medium exchanges heat with the refrigerant circulating in 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 self-heating of the inverter 61, the motor generator 62, and the transaxle device 63 can be circulated via the bypass passage 44d.

Therefore, in the vehicle air conditioner 1 in the heating mode, the vehicle interior 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.

Also, 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 .

(3) Dehumidification/heating mode The dehumidification/heating mode is an operation mode in which dehumidification/heating is performed in the passenger compartment without cooling the battery 60 .

In the dehumidifying and heating mode, the control device 70 switches the refrigeration cycle device 10 to the refrigerant circuit in the dehumidifying and heating mode. Specifically, the control device 70 causes the first expansion valve 17a to be throttled. Based on the detection signals transmitted from the second refrigerant temperature sensor 19b and the second refrigerant pressure sensor 19e, the controller 70 adjusts the degree of superheat of the refrigerant on the outlet side of the indoor evaporator 14 to a predetermined target degree of superheat. , determines the degree of opening of the first expansion valve 17a.

In addition, the control device 70 brings the second expansion valve 17b into a throttled state or a fully closed state according to the target temperature in the passenger compartment set by the temperature setting switch. When the second expansion valve 17b is throttled, the control device 70 supercools the refrigerant on the outlet side of the chiller 16 based on the detection signals transmitted from the third refrigerant temperature sensor 19c and the third refrigerant pressure sensor 19f. The degree of opening is determined so that the degree of supercooling reaches a predetermined target degree of supercooling.

Further, the control device 70 adjusts the rotational position of the valve body of the high temperature side flow control valve 33 so that the high temperature side heat medium flowing into the high temperature side flow control valve 33 flows out to the high temperature side radiator 34 and the heater core 35 . The control device 70 adjusts the rotational position of the valve body of the high-temperature side flow control valve 33 according to the target temperature in the passenger compartment set by the temperature setting switch, and the air flows out to the high-temperature side radiator 34 and the heater core 35 respectively. Change the flow rate of the high temperature side heat medium.

Further, when the second expansion valve 17b is throttled, the control device 70 prevents the low-temperature side heat medium flowing into the battery-side three-way valve 42 from flowing out to the cooling water passage of the battery 60, and only to the low-temperature side radiator 43. The rotational position of the valve body of the battery side three-way valve 42 is adjusted so that the liquid flows out. When the second expansion valve 17b is fully closed, the control device 70 fully closes the battery-side three-way valve 42 as well.

Then, the control device 70 adjusts the rotational position of the valve element of the device side three-way valve 44c so that the low temperature side heat medium flowing into the device 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 element of the device-side three-way valve 44c based on the detection signal transmitted from the third low-temperature side heat medium temperature sensor 47c, so that the low-temperature side radiator 43 and the bypass passage 44d are supplied with heat. Adjust the flow rate of the low-temperature side heat transfer medium to be introduced.

In addition, the control device 70 operates the electric actuator of the air mix door 56 so that the temperature of the air blown into the passenger compartment approaches the target blowout temperature, and the air is passed through the heater core 35 side and the cold air bypass passage 55. adjust the air volume. Further, the control device 70 controls the electric power supply based on the 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. The heating capacity of the heater 32 is adjusted as required.

Then, 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. Further, the control device 70 outputs a control signal to operate the high-temperature side heat medium pump 31, the device pump 44b, and the blower 53. FIG. Note that the control device 70 outputs a control signal for operating the low temperature side heat medium pump 41 when the second expansion valve 17b is in the throttled state, and when the second expansion valve 17b is in the fully closed state, , the control signal for operating the low temperature side heat medium pump 41 is not output.

Therefore, in the refrigeration cycle device 10 in the dehumidifying and heating mode, the compressor 12→water-refrigerant heat exchanger 13→refrigerant branch portion 18→first expansion valve 17a→indoor evaporator 14→air conditioning inflow pipe 11a→connecting device 100→compression Refrigerant circulates in the order of machine outflow pipe 11c→compressor 12 .

In addition, in the refrigeration cycle device 10 in the dehumidifying and heating mode, when the second expansion valve 17b is throttled, the refrigerant branches at the refrigerant branch portion 18 and flows. In this case, in the refrigerating cycle device 10, the refrigerant branched at the refrigerant branching portion 18 flows through the second expansion valve 17b→chiller 16→cooling portion inflow pipe 11b→connecting device 100→compressor outflow pipe 11c→compressor 12 in this order.

In the refrigeration cycle device 10 in the dehumidifying and heating mode, when the second expansion valve 17b is fully closed, no refrigerant flows into the cooling section inflow pipe 11b.

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 from the high temperature side radiator 34 and heater core 35 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 .

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 pump 41 causes the low-temperature side heat medium flowing out of the water passage of the chiller 16 to flow into the low-temperature side radiator. 43 and returns to the suction port of the low temperature side heat medium pump 41 . Further, in the low-temperature side heat medium circuit 40 in the dehumidification/heating mode, the low-temperature side heat medium flows in the order of the device 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 device 63. , into the device-side three-way valve 44c. Then, the low temperature side heat medium flowing into the device side three-way valve 44c flows to the low temperature side radiator 43 and the bypass passage 44d according to the rotational position of the valve body of the device side three way valve 44c, and flows into the suction port of the device side pump 44b. back to

In this manner, in the dehumidifying and heating mode, the refrigerant flowing out of the indoor evaporator 14 flows into the connection device 100 from the rapid flow inlet 121 through the air conditioning inflow pipe 11a. Further, when the second expansion valve 17b is in the throttled state, the refrigerant that has flowed out of the chiller 16 flows into the connecting device 100 from the low inlet 131 through the cooling section inflow pipe 11b. On the other hand, when the second expansion valve 17b is fully closed, the refrigerant does not flow into the connection device 100 from the low inlet 131 .

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 flow outlet 143 and lead to the compressor flow outflow pipe 11c.

Further, in the refrigeration cycle device 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 exchanges water-refrigerant heat. The refrigerant flowing out of the vessel 13 is decompressed. In the refrigerating cycle device 10, the indoor evaporator 14 absorbs heat from the air blown from the blower 53, evaporates the refrigerant, and cools and dehumidifies the air.

Further, in the refrigeration cycle device 10 in the dehumidifying and heating mode, the second expansion valve 17b reduces the pressure of the refrigerant flowing out of the water-refrigerant heat exchanger 13 when the second expansion valve 17b is in the throttled state. In the refrigeration cycle device 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.

Also, in the high temperature side heat medium circuit 30 in the dehumidification heating mode, the high temperature side radiator 34 radiates heat from the high temperature side heat medium heated by the water-refrigerant heat exchanger 13 . Furthermore, in the high temperature side heat medium circuit 30 in the dehumidification 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 air blown from the blower 53 in the heater core 35. , to heat the blast air.

In addition, 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 heated by absorbing heat from the outside air flows into the chiller 16 as in the heating mode. to heat the refrigerant. Further, in the low-temperature side heat medium circuit 40 in the dehumidifying and heating mode, part of the flow rate of the low-temperature side heat medium heated by self-heating of the inverter 61, the motor generator 62, and the transaxle device 63 flows into the bypass passage 44d, The rest of the flow is sent to the low temperature side radiator 43 .

Therefore, in the vehicle air conditioner 1 in the dehumidification/heating mode, the blown air that has been cooled and dehumidified by the indoor evaporator 14 and reheated by the heater core 35 is blown into the vehicle interior. Thereby, the vehicle air conditioner 1 can dehumidify and heat the vehicle interior.

Further, 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. Furthermore, by circulating the low temperature side heat medium cooled by the low temperature side radiator 43 in the low temperature side heat medium circuit 40, the inverter 61, the motor generator 62, and the transaxle device 63 can be cooled or heated. .

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

In the cooling mode, the control device 70 switches the refrigeration cycle device 10 to the cooling mode refrigerant circuit. Specifically, the control device 70 brings the first expansion valve 17a into the fully closed state and the second expansion valve 17b into the throttle state. The controller 70 adjusts the degree of supercooling of the refrigerant on the outlet side of the chiller 16 to a predetermined target degree of supercooling based on the detection signals transmitted from the third refrigerant temperature sensor 19c and the third refrigerant pressure sensor 19f. , determines the degree of opening of the second expansion valve 17b.

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

Further, the control device 70 adjusts the rotational position of the valve body 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 cooling water passage of the battery 60 . The control device 70 adjusts the rotational position of the valve element of the battery side three-way valve 42 based on the detection signal transmitted from the first low temperature side heat medium temperature sensor 47 a , thereby controlling the low temperature that flows into the cooling water passage of the battery 60 . Change the flow rate of the side heating medium.

Then, the control device 70 adjusts the rotational position of the valve body of the device side three-way valve 44c so that the low temperature side heat medium flowing into the device side three way valve 44c does not flow out to the bypass passage 44d but flows out only to the low temperature side radiator 43. adjust. Further, the control device 70 outputs a control signal 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.

Therefore, in the cooling mode refrigeration cycle device 10, the compressor 12→water-refrigerant heat exchanger 13→refrigerant branch portion 18→second expansion valve 17b→chiller 16→cooling portion inflow pipe 11b→connection device 100→compressor outflow The refrigerant circulates in the order of piping 11c→compressor 12 . Since the first expansion valve 17a is fully closed in the refrigeration cycle apparatus 10 in the cooling mode, the refrigerant does not flow into the air conditioning inflow pipe 11a.

In the high-temperature side heat medium circuit 30 in the cooling mode, the high-temperature side heat medium flowing out of the water passage of the water-refrigerant heat exchanger 13 flows to the high-temperature side radiator 34 by the high-temperature side heat medium pump 31. Return to the inlet of pump 31 .

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 cooling water passage of the battery 60, and the low-temperature side heat medium pump 41 Return to intake. In addition, in the low temperature side heat medium circuit 40 in the cooling mode, 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 device 63→the low temperature side radiator 43→the equipment pump The low temperature side heat medium circulates in the order of 44b.

Thus, in the cooling mode, the refrigerant flowing out of the chiller 16 flows into the connection device 100 through the low inlet 131 through the cooling section inlet pipe 11b, but does not flow through the rapid inlet 121. FIG. 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 pipe 11c.

Further, in the cooling mode refrigeration cycle device 10, 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 is a water-refrigerant heat exchanger. The refrigerant flowing out from 13 is decompressed. In the refrigerating cycle device 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.

Also, in the high temperature side heat medium circuit 30 in the cooling mode, the high temperature side radiator 34 heats the high temperature side heat medium heated by the water-refrigerant heat exchanger 13 . Then, in the low temperature side heat medium circuit 40 in the cooling mode, the low temperature side heat medium cooled by the chiller 16 absorbs heat from the battery 60 in the cooling water 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 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, respectively.

Therefore, in the vehicle air conditioner 1 in the cooling mode, the low temperature side heat medium cooled by the chiller 16 can be circulated through the cooling water passage of the battery 60 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 in the low temperature side heat medium circuit 40 to operate the inverter 61, the motor generator 62, and the transaxle device 63. Allow to cool.

By the way, the vehicle air conditioner 1 of the present embodiment executes an operation mode in which a cooling mode is combined with each air conditioning mode under operating conditions that require cooling of the battery 60 when operating in each of the air conditioning modes described above. can do. An operating condition that requires cooling of the battery 60 is, for example, a case where the temperature of the battery 60 becomes higher than a predetermined battery reference temperature due to operation of the battery 60 .

As an example of an operation mode in which the cooling mode is combined with the air conditioning mode, the cooling mode in which the cooling mode is combined with the cooling mode will be described below. The vehicle air conditioner 1 of the present embodiment can also operate in an operation mode in which a heating mode is combined with a cooling mode and an operation mode in which a dehumidifying heating mode is combined with a cooling mode.

(5) Air-cooling mode The air-cooling mode is an operation mode in which the vehicle interior is cooled and the battery 60 is cooled.

In the cooling cooling mode, the control device 70 switches the refrigeration cycle device 10 to the refrigerant circuit in the cooling cooling mode. Specifically, the control device 70 causes the first expansion valve 17a and the second expansion valve 17b to be throttled.

Based on the detection signals transmitted from the second refrigerant temperature sensor 19b and the second refrigerant pressure sensor 19e, the controller 70 adjusts the degree of superheat of the refrigerant on the outlet side of the indoor evaporator 14 to a predetermined target degree of superheat. , determines the degree of opening of the first expansion valve 17a. Further, the controller 70 controls the degree of subcooling of the refrigerant on the outlet side of the chiller 16 to reach a predetermined target degree of supercooling based on the detection signals transmitted from the third refrigerant temperature sensor 19c and the third refrigerant pressure sensor 19f. Thus, the opening degree of the second expansion valve 17b is determined.

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

Further, the control device 70 adjusts the rotational position of the valve body 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 cooling water passage of the battery 60 . The control device 70 adjusts the rotational position of the valve element of the battery side three-way valve 42 based on the detection signal transmitted from the first low temperature side heat medium temperature sensor 47 a , thereby controlling the low temperature that flows into the cooling water passage of the battery 60 . Change the flow rate of the side heating medium.

Then, the control device 70 adjusts the rotational position of the valve body of the device side three-way valve 44c so that the low temperature side heat medium flowing into the device side three way valve 44c does not flow out to the bypass passage 44d but flows out only to the low temperature side radiator 43. adjust.

In addition, the control device 70 operates the electric actuator of the air mix door 56 so that the total amount of blown air that has passed through the indoor evaporator 14 passes through the cold air bypass passage 55 . Then, the control device 70 outputs a control signal 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. FIG.

Therefore, in the refrigeration cycle device 10 in the cooling cooling mode, the refrigerant flows in the order of the compressor 12→water-refrigerant heat exchanger 13→refrigerant branching section 18 and is branched at the refrigerant branching section 18. FIG. One of the refrigerants branched at the refrigerant branching portion 18 flows through the first expansion valve 17a→indoor evaporator 14→air conditioning inflow pipe 11a→connecting device 100→compressor outflow pipe 11c→compressor 12 in this order. The other refrigerant branched at the refrigerant branching portion 18 flows through the second expansion valve 17b→chiller 16→cooling portion inflow pipe 11b→connecting device 100→compressor outflow pipe 11c→compressor 12 in this order.

In addition, in the high temperature side heat medium circuit 30 in the cooling cooling mode, the high temperature side heat medium flowing out of the water passage of the water-refrigerant heat exchanger 13 flows to the high temperature side radiator 34 by the high temperature side heat medium pump 31, and the high temperature side heat is generated. Return to the inlet side of the medium pump 31 .

In the low-temperature side heat medium circuit 40 in the cooling 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 cooling water passage of the battery 60 . back to the inhaler. In addition, in the low temperature side heat medium circuit 40 in the cooling cooling mode, 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 device 63→the low temperature side radiator 43→the equipment The low temperature side heat medium circulates in order of the pump 44b.

Thus, in the cooling cooling mode, the refrigerant flowing out of the indoor evaporator 14 flows into the connection device 100 from the rapid flow inlet 121 through the air conditioning inflow pipe 11a. Further, in the connecting device 100, the refrigerant that has flowed out of the chiller 16 flows in from the low inlet 131 through the cooling section inflow pipe 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 flow outlet 143 and lead to the compressor flow outflow pipe 11c.

Further, in the refrigeration cycle device 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 reduces the pressure of the refrigerant flowing out of the water-refrigerant heat exchanger 13 . In the refrigeration cycle device 10, the indoor evaporator 14 absorbs heat from the air blown from the blower 53, evaporates the refrigerant, and cools the air. Furthermore, in the refrigerating cycle device 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.

In the high temperature side heat medium circuit 30 in the cooling cooling mode, the high temperature side radiator 34 radiates heat from the high temperature side heat medium heated by the water-refrigerant heat exchanger 13 .

Then, in the low temperature side heat medium circuit 40 in the cooling cooling mode, the low temperature side heat medium cooled by the chiller 16 absorbs heat from the battery 60 in the cooling water 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 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, respectively.

Therefore, in the vehicle air conditioner 1 in the cooling cooling mode, the vehicle interior can be cooled by blowing out the blown air cooled by the indoor evaporator 14 into the vehicle interior. Furthermore, the low temperature side heat medium cooled by the chiller 16 can be circulated through the cooling water passage of the battery 60 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 in the low temperature side heat medium circuit 40 to operate the inverter 61, the motor generator 62, and the transaxle device 63. Allow to cool.

Next, details of the connection device 100 will be described with reference to FIGS. 3 to 11. FIG. 3 and the like indicate the vertical direction DR1 with reference to the direction of gravity when the connection device 100 is used. 3 and the like indicate the front-rear direction DR2 and the left-right direction DR3 with reference to the forward direction determined for convenience in the connection device 100. As shown in FIG. Note that the vertical direction DR1 does not limit the orientation of the connection device 100 when the connection device 100 is not actually used, such as during manufacture, sale, or transportation. Further, the front-rear direction DR2 and the left-right direction DR3 do not limit the attitude of the connection device 100 . 4 shows a cross-sectional shape of a plane passing through the center of the connection device 100 in the front-rear direction DR2 and perpendicular to the front-rear direction DR2.

As shown in FIGS. 3 and 4, the connection device 100 includes a housing 110, a rapid upstream flow path portion 120, a low upstream flow path portion 130, and a downstream flow path portion, which are refrigerant passages formed inside the housing 110. 140 is provided.

The housing 110 extends in the front-rear direction DR2 and has a pentagonal prism shape in which a cross-sectional shape of a surface orthogonal to the front-rear direction DR2 is a pentagonal shape, and is made of, for example, a resin material. Housing 110 includes a bottom surface portion 111 provided on the lower side in vertical direction DR1, and right and left side portions 112 and 112 extending upward along vertical direction DR1 from both side ends of bottom surface portion 111 in horizontal direction DR3. 113.

Furthermore, the housing 110 has a right slope portion 114 that slopes leftward in the horizontal direction DR3 and extends upward in the vertical direction DR1 from the upper end portion of the right side surface portion 112 in the vertical direction DR1. Further, the housing 110 has a left slope portion 115 that slopes to the right in the left-right direction DR3 and extends upward in the up-down direction DR1 from the upper end portion of the left side surface portion 113 in the up-down direction DR1.

In the cross-sectional shape of the surface orthogonal to the front-rear direction DR2, the right slanted portion 114 and the left slanted portion 115 are symmetrical about a straight line passing through the center of the bottom surface portion 111 in the left-right direction DR3 and extending along the up-down direction DR1. and the angles of inclination to each other are the same. In addition, the end of the right slope portion 114 opposite to the side where the right side portion 112 is connected continues to the end of the left slope portion 115 opposite to the side where the left side portion 113 is connected. Note that the housing 110 may be made of a metal material such as aluminum.

As shown in FIG. 4 , inside the housing 110 , there is formed a steep upstream channel portion 120 that extends from the surface of the right slope portion 114 toward the bottom portion 111 without passing through the bottom portion 111 . Further, inside the housing 110, a low upper flow path portion 130 is formed that extends from the surface of the left slope portion 115 toward the right side portion 112 to the right side portion 112 without penetrating therethrough. Further, inside the housing 110, a downstream flow passage portion 140 is formed that extends from the surface of the bottom surface portion 111 toward the upper side in the vertical direction DR1 to the right slope portion 114 and the left slope portion 115 without penetrating therethrough.

Rapid upstream flow path portion 120 extends from a portion of the surface of right slope portion 114 above the center in vertical direction DR1 toward a portion on the left side of the center in horizontal direction DR3 of bottom surface portion 111 . Further, the steep upstream flow path portion 120 is provided at the end opposite to the side positioned on the surface of the right slope portion 114 among both ends of the steep upstream flow path portion 120 , and , opposite to the side positioned on the surface of the bottom surface 111 are connected. That is, the steep upstream channel portion 120 is connected to the lower end of the steep upstream channel portion 120 in the vertical direction DR1 and the upper end of the downstream channel portion 140 in the vertical direction DR1.

Low upper flow path portion 130 extends from a portion of the surface of left slope portion 115 below the center in vertical direction DR1 toward a portion below the center in vertical direction DR1 of right side portion 112 . Further, the low upstream flow path portion 130 is provided at the end opposite to the side positioned on the surface of the left slope portion 115 among both end portions of the low upstream flow path portion 130 , different from both ends of the downstream flow path portion 140 . Intermediate portions of different refrigerant passages are connected. That is, the lower upstream flow path portion 130 is provided at the lower end of the lower upstream flow path portion 130 in the vertical direction DR1, and the portion between the upper end and the lower end of the downstream flow path portion 140 in the vertical direction DR1. is connected.

The steep upstream channel portion 120 and the low upstream channel portion 130 are not directly connected to each other, but are connected via the downstream channel portion 140 . Therefore, the refrigerant flowing through the low upstream flow path portion 130 does not directly join the refrigerant flowing through the steep upstream flow path portion 120 . In this embodiment, the steep upstream channel portion 120 functions as a first inclined upstream channel portion, and the low upstream channel portion 130 functions as a second inclined upstream channel portion.

The rapid upstream passage portion 120 forms a refrigerant passage for guiding the refrigerant flowing out of the air-conditioning inflow pipe 11a into the housing 110, and is connected to the air-conditioning inflow pipe 11a one-to-one. The rapid upstream flow path portion 120 has a rapid flow inlet 121 that allows the refrigerant to flow into the rapid upstream flow path portion 120 on the upstream side of the refrigerant flow, and has a rapid confluence port 122 that communicates with the downstream flow path portion 140 on the downstream side of the refrigerant flow.

Further, the steep upstream channel portion 120 extends linearly along a direction different from the direction in which the downstream channel portion 140 extends. The direction in which the steep upstream channel portion 120 extends will be described later.

The rapid upstream channel portion 120 has a first inner diameter φ1, which is the inner diameter of the rapid upstream channel portion 120, slightly larger than the outer diameter of the air conditioning inflow pipe 11a. 11a can be inserted.

The steep upstream channel portion 120 is formed such 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 the cross-sectional shape in the direction orthogonal to the direction in which the steep upstream flow path portion 120 extends.

The lower upper flow path portion 130 forms a refrigerant passage for guiding the refrigerant flowing out of the cooling portion inflow pipe 11b into the housing 110, and is connected to the cooling portion inflow pipe 11b in a one-to-one manner. The low upstream channel portion 130 has a low inlet port 131 that allows the coolant to flow into the low upstream channel portion 130 on the upstream side of the coolant flow, and has a low confluence port 132 that communicates with the downstream channel portion 140 on the downstream side of the coolant flow. .

Further, the low upstream channel portion 130 extends linearly in a direction different from the direction in which the downstream channel portion 140 extends and the direction in which the steep upstream channel portion 120 extends. The direction in which the low upper flow path portion 130 extends will be described later.

The lower upper flow path portion 130 has a second inner diameter φ2, which is the inner diameter of the lower upper flow path portion 130, slightly larger than the outer diameter of the cooling portion inflow pipe 11b. It is formed so that the inflow pipe 11b can be inserted.

The lower upper flow path portion 130 is formed such that the second inner diameter φ2 is uniform from the refrigerant flow upstream side to the refrigerant flow downstream side. The second inner diameter φ2 is the diameter of the cross-sectional shape in the direction perpendicular to the direction in which the low upper flow path portion 130 extends. In this embodiment, the first inner diameter φ1 and the second inner diameter φ2 are formed to have the same size.

The downstream channel portion 140 forms a coolant channel for causing the coolant that has flowed into the housing 110 through the steep upstream channel portion 120 and the low upstream channel portion 130 to flow out of the housing 110 . be. The downstream channel portion 140 is connected one-to-one with the compressor outflow pipe 11c.

The downstream channel portion 140 has a first confluence portion 141 that joins the coolant flowing through the steep upstream channel portion 120 to the downstream channel portion 140 on the upstream side of the coolant flow. Further, the downstream channel portion 140 has a second confluence portion 142 that joins the coolant flowing through the low upstream channel portion 130 into the downstream channel portion 140 on the refrigerant flow downstream side of the first confluence portion 141 . The downstream channel portion 140 has a refrigerant outlet 143 into which the compressor outlet pipe 11c is inserted on the most downstream side of the refrigerant flow.

Downstream channel portion 140 extends linearly along vertical direction DR1 from substantially the center of the surface of bottom surface portion 111 toward a portion where right slope portion 114 and left slope portion 115 are connected. That is, the direction in which the downstream flow path portion 140 of the present embodiment extends does not include the left-right direction DR3 and the front-rear direction DR2, but along the up-down direction DR1.

Here, a straight line L1 passing through the center of the refrigerant outlet 143 and along the direction in which the downstream channel portion 140 extends intersects with a straight line L2 passing through the center of the rapid inlet 121 and along the direction in which the rapid upstream channel portion 120 extends. A first junction portion 141 is defined as a portion where the junction is formed. Further, a straight line L1 passing through the center of the refrigerant outlet port 143 and extending along the direction in which the downstream channel portion 140 extends intersects with a straight line L3 passing through the center of the low inlet port 131 and along the direction in which the low upper channel portion 130 extends. A second confluence portion 142 is defined as a portion where the two merge.

In the present embodiment, the first confluence portion 141 and the second confluence portion 142 are provided at different positions in the downstream channel portion 140 . Specifically, the first merging portion 141 is provided at a position on the upstream side of the flow of the refrigerant in the downstream channel portion 140 relative to the second merging portion 142 . The first confluence portion 141 is a portion into which the refrigerant flowing through the rapid upstream flow path portion 120 flows.

The second confluence portion 142 combines the refrigerant flowing from the rapid upstream flow path portion 120 into the downstream flow path portion 140 via the first confluence portion 141 and the refrigerant flowing into the downstream flow path portion 140 from the low upstream flow path portion 130 . It is the part that flows. In this embodiment, the first confluence section 141 and the second confluence section 142 function as confluence sections.

In the downstream channel portion 140, the refrigerant outlet 143, which is the most downstream side of the refrigerant flow, is provided at a position below the rapid flow inlet 121, which is the most upstream side of the refrigerant flow of the rapid upstream channel portion 120, in the vertical direction DR1. It is Furthermore, the downstream channel portion 140 has a refrigerant outlet port 143 located below the low inlet port 131, which is the most upstream side of the refrigerant flow of the low upstream channel portion 130, in the vertical direction DR1. In other words, the refrigerant outlet 143 is positioned vertically below the rapid inlet 121 and the low inlet 131 .

Also, the coolant outlet 143 is formed in the bottom surface portion 111 so that the opening direction is downward in the vertical direction. 5, when the connection device 100 is applied to the vehicle air conditioner 1, the refrigerant outflow port 143 is positioned above the refrigerant suction port 12a of the compressor 12 in the vertical direction. placed in position.

The downstream channel portion 140 is formed such that the third inner diameter φ3, which is the inner diameter of the downstream channel portion 140, is slightly larger than the outer diameter of the compressor outflow pipe 11c. It is formed so that the compressor outflow pipe 11c can be inserted therein.

The downstream channel portion 140 is formed such that the third inner diameter φ3 is the same from the first junction portion 141 to the refrigerant outlet port 143 via the second junction portion 142 . The third inner diameter φ3 is the diameter of the cross-sectional shape in the direction perpendicular to the direction in which the downstream flow path portion 140 extends. Also, 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 path portion 140 has an inner diameter larger than the first inner diameter φ1 on the downstream side of the refrigerant flow from the first merging portion 141, and has an inner diameter of the second inner diameter on the downstream side of the refrigerant flow from the second merging portion 142. It is formed larger than the inner diameter φ2.

In other words, the downstream channel portion 140 has a channel cross-sectional area in a direction orthogonal to the coolant flow direction on the downstream side of the coolant flow from the first confluence portion 141 . is larger than the channel cross-sectional area of the cross section in the direction perpendicular to the In addition, the downstream channel portion 140 has a channel cross-sectional area in a direction perpendicular to the coolant flow direction on the downstream side of the coolant flow from the second confluence portion 142 . It is larger than the channel cross-sectional area of the cross section in the direction of

Here, the ratio of the inner diameter of the downstream channel portion 140 to the inner diameter of the steep upstream channel portion 120 and the inner diameter of the low upstream channel portion 130 will be described with reference to the graph of FIG. The pressure loss when the refrigerant passes through the connection device 100 and the manufacturing cost of the connection device 100 depend on the ratio of the inner diameter of the downstream channel portion 140 to the inner diameter of the steep upstream channel portion 120 and the inner diameter of the low upstream channel portion 130. Change. As described above, in the present embodiment, the inner diameter of the rapid upstream channel portion 120 is the first inner diameter φ1, the inner diameter of the low upstream channel portion 130 is the second inner diameter φ2, and the inner diameter of the downstream channel portion 140 is the third inner diameter. φ3.

The connecting device 100 has a third inner diameter φ3 larger than the first inner diameter φ1 and the second inner diameter φ2. By the way, the speed of the coolant flowing through the downstream flow passage portion 140 becomes lower as the inner diameter of the downstream flow passage portion 140 increases. Therefore, the velocity of the coolant flowing through the downstream flow path portion 140 is greater than the first inner diameter φ1 and the second inner diameter φ2, and is equal to the first inner diameter φ1 and the second inner diameter φ2. slow in comparison. Then, the speed of the coolant flowing through the downstream channel portion 140 becomes slower as the third inner diameter φ3 is larger than the first inner diameter φ1 and the second inner diameter φ2.

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

Moreover, the pressure loss caused by the refrigerant flowing through the downstream flow passage portion 140 decreases as the speed of the refrigerant flowing through the downstream flow passage portion 140 decreases. Therefore, as shown in FIG. 6, the pressure loss generated 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 will also be referred to as the connecting portion diameter ratio σ.

On the other hand, from the viewpoint of the manufacturing cost of the connection device 100, when forming the refrigerant passage inside the connection device 100, the steep upstream flow path portion 120 and the low upstream flow path portion 130, and the downstream flow path portion 140 are the same. It is most desirable to form it with an inner diameter. In order to form the steep upstream channel portion 120, the low upstream channel portion 130, and the downstream channel portion 140 with different inner diameters, for example, a tool or the like is required for forming coolant channels of different sizes. This is because it becomes a factor of cost increase.

Therefore, as shown in FIG. 6, the manufacturing cost of the connection device 100 is as follows. be the smallest. 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 the connecting device 100 is the lowest.

However, in this embodiment, as described above, the compressor outflow pipe 11c has a larger outer diameter than the air conditioning inflow pipe 11a and the cooling part inflow pipe 11b. For this reason, if the first inner diameter φ1, the second inner diameter φ2, and the third inner diameter φ3 are of the same size, the refrigerant outlet 143 is connected to the compressor outlet pipe 11c. It is necessary to take measures such as attaching a refrigerant pipe converting member having a different diameter to the refrigerant outlet 143 . This is not preferable because it causes an increase in the manufacturing cost of the connection device 100 when measures such as installing a refrigerant pipe conversion member are included in the manufacturing cost of the connection device 100 .

On the other hand, the inner diameter of the rapid upstream channel portion 120 corresponds to the outer diameter of the air conditioning inlet pipe 11a, the inner diameter of the low upstream channel portion 130 corresponds to the outer diameter of the cooling portion inlet pipe 11b, and the downstream channel portion 140 corresponds to the outer diameter of the cooling portion inlet pipe 11b. corresponds to the outer diameter of the compressor outflow pipe 11c. In this case, there is a factor of increased manufacturing cost for forming refrigerant passages with different inner diameters, but since it is not necessary to attach a refrigerant pipe conversion member, etc., the increase in manufacturing cost of the connection device 100 as a whole is compared. can be effectively suppressed.

For this reason, in the present embodiment, the inner diameter of the rapid upstream channel portion 120, that is, the first inner diameter φ1 is formed to have a size corresponding to the outer diameter of the air conditioning inflow pipe 11a. Specifically, the inner diameter of the steep upstream channel portion 120 is formed slightly larger than the outer diameter of 15.88 mm of the air conditioning inflow pipe 11a so that the air conditioning inflow pipe 11a can be inserted. In other words, the inner diameter of the portion of the rapid upstream channel portion 120 to which the air conditioning inflow pipe 11a is connected is formed to have a size corresponding to the most downstream portion of the refrigerant flow of the air conditioning inflow pipe 11a.

In addition, the inner diameter of the lower upstream flow path portion 130, that is, the second inner diameter φ2 is formed to have a size corresponding to the outer diameter of the cooling section inflow pipe 11b so that the cooling section inflow pipe 11b can be inserted. Specifically, the inner diameter of the lower upper flow path portion 130 is formed slightly larger than the outer diameter of 15.88 mm of the cooling portion inflow pipe 11b. In other words, the inner diameter of the portion of the lower upstream flow path portion 130 to which the cooling portion inflow pipe 11b is connected is formed to have a size corresponding to the refrigerant flow most downstream portion of the cooling portion inflow pipe 11b.

The inner diameter of the downstream channel portion 140, that is, the third inner diameter φ3 is formed to have a size corresponding to the outer diameter of the compressor outflow pipe 11c. Specifically, the inner diameter of the downstream channel portion 140 is formed slightly larger than the outer diameter of 19.05 mm of the compressor outflow pipe 11c so that the compressor outflow pipe 11c can be inserted. In other words, the inner diameter of the portion of the downstream channel portion 140 to which the compressor outflow pipe 11c is connected is formed to have a size corresponding to the most upstream portion of the refrigerant flow of the compressor outflow pipe 11c. The value of the connecting portion diameter ratio σ of this embodiment determined in this way is 1.20.

As described above, as shown in FIG. 6, as the value of the connecting portion diameter ratio σ becomes larger than 1, the manufacturing cost of the connecting device 100 increases. , the increase in manufacturing cost can be relatively suppressed. In the range where the connecting portion diameter ratio σ is 1 or more and 1.20 or less, the magnitude of the increase in manufacturing cost due to the increase in the connecting portion diameter ratio σ is the decrease in pressure loss due to the increase in the connecting portion diameter ratio σ. smaller than the size of

Therefore, as in the present embodiment, by setting the first inner diameter φ1, the second inner diameter φ2, and the third inner diameter φ3 so that the value of the connecting portion diameter ratio σ is about 1.20, the pressure loss can be reduced. While suppressing, the manufacturing cost of the connection device 100 can be relatively suppressed.

Further, let us assume that the inner diameter of the downstream channel portion 140 is made larger than the size corresponding to the outer diameter of the compressor outflow pipe 11c in order to make the value of the connecting 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 cost due to the formation of refrigerant passages with different inner diameters inside the connection device 100, the compressor discharge pipe 11c must be connected to the refrigerant discharge port 143. Therefore, it is also necessary to install a refrigerant pipe conversion member for this purpose.

Therefore, the manufacturing cost of the connection device 100 sharply increases when the value of the connection portion diameter ratio σ exceeds 1.20. In other words, when the first inner diameter φ1 corresponds to the outer diameter of the air conditioning inflow pipe 11a and the second inner diameter φ2 corresponds to the outer diameter of the cooling section inflow pipe 11b, the third inner diameter φ3 corresponds to the outer diameter of the compressor outflow pipe 11c. The manufacturing cost increases as the size becomes larger than the size corresponding to the outer diameter. In the range where the value of the connecting portion diameter ratio σ is greater than 1.20, the magnitude of the increase in manufacturing cost accompanying an increase in the connecting portion diameter ratio σ is the decrease in pressure loss accompanying an increase in the connecting portion diameter ratio σ. much larger than the size of

Therefore, when the first inner diameter φ1 corresponds to the outer diameter of the air conditioning inflow pipe 11a and the second inner diameter φ2 corresponds to the outer diameter of the cooling unit inflow pipe 11b, the value of the connecting portion diameter ratio σ is about 1.20. It is desirable to set the third inner diameter φ3 so that

Subsequently, the details of the direction in which the steep upstream channel portion 120 and the low upstream channel portion 130 extend will be described using the direction in which the downstream channel portion 140 extends. Here, the direction along the vertical direction DR1 and extending from the first merging portion 141 and the second merging portion 142 toward the downstream side of the downstream flow passage portion 140 is defined as the downstream direction. sets the opposite direction as a predetermined confluence reference direction DRC. The predetermined confluence reference direction DRC is an upward direction along the vertical direction DR1 with respect to the first confluence portion 141 and the second confluence portion 142 .

As shown in FIG. 4 , the steep upstream flow path portion 120 extends at a first angle θ1 greater than 0° and less than 90° with respect to the predetermined confluence reference direction DRC, with the first confluence portion 141 as a reference. there is Here, the angle extending from the first confluence portion 141 deviated from the predetermined confluence reference direction DRC means that the upper side of the vertical direction DR1 is 0° and the clockwise direction is the positive direction in the cross-sectional view shown in FIG. is the angle for The first angle θ1 is an angle formed by the predetermined confluence reference direction DRC and the direction in which the steep upstream channel portion 120 extends, with the first confluence portion 141 as the center.

In this embodiment, the steep upstream flow path portion 120 extends so that the first angle θ1 is greater than 0° and less than 90° (30° in this embodiment). In this manner, the steep upstream flow path portion 120 extends from the first confluence portion 141 toward the upper side in the vertical direction DR1 and the right side in the horizontal direction DR3 with a deviation of 30° from the predetermined confluence reference direction DRC. The direction in which steep upstream flow path portion 120 extends includes left-right direction DR3 and up-down direction DR1, but does not include front-back direction DR2.

Note that the steep upstream flow path portion 120 may be configured such that the first angle θ1 is larger than 30° (eg, 80°) or smaller than 30° (eg, 20°). However, it is desirable that the first angle θ1 be an angle that is larger than 0° and smaller than 90° and is as small as possible. For example, the first angle θ1 is desirably 65° or less. Furthermore, it is desirable that the first angle θ1 is 45° or less.

On the other hand, the low upstream flow path portion 130 extends at a second angle θ2 greater than 0° and less than 90° with respect to the predetermined confluence reference direction DRC with the second confluence portion 142 as a reference. Here, the angle extending from the second confluence portion 142 deviated from the predetermined confluence reference direction DRC means that the upper side of the vertical direction DR1 is 0° and the counterclockwise direction is positive in the cross-sectional view shown in FIG. This is the angle to be oriented. The second angle θ2 is an angle formed by the predetermined confluence reference direction DRC and the direction in which the low upstream flow path portion 130 extends, with the second confluence portion 142 as the center.

In the present embodiment, the low upstream flow path portion 130 is arranged such that the second angle θ2 is greater than 0° and less than 90° and greater than the first angle θ1 (60° in this embodiment). is extended. In this manner, the low upstream flow path portion 130 extends from the second confluence portion 142 toward the upper side in the vertical direction DR1 and the left side in the horizontal direction DR3 with a deviation of 60° from the predetermined confluence reference direction DRC. The direction in which the low upper flow path portion 130 extends includes the left-right direction DR3 and the up-down direction DR1, but does not include the front-rear direction DR2.

In addition, if the low upstream flow path portion 130 is larger than the first angle θ1, the second angle θ2 is an angle larger than 60° (eg, 85°) or an angle smaller than 60° (eg, 50°). It may be configured as follows. However, it is desirable that the second angle θ2 be an angle that is larger than 0° and smaller than 90° and is as small as possible. For example, it is desirable that the second angle θ2 is 80° or less. Furthermore, it is desirable that the second angle θ2 is 70° or less.

Also, the angle formed by the straight line L1 and the straight line 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.

Next, in the connection device 100 having the above configuration, the flow of refrigerant flowing inside the housing 110 when the refrigeration cycle device 10 operates in each operation mode will be described with reference to FIGS. 7 to 9. FIG.

As described above, in the cooling mode, refrigerant flows into the connecting device 100 from the rapid inlet 121 through the air conditioning inlet pipe 11a, but no refrigerant flows from the low inlet 131 . Further, in the dehumidifying and heating mode, when the second expansion valve 17b is fully closed, the refrigerant flows into the connection device 100 from the rapid inlet 121 through the air conditioning inlet pipe 11a, whereas the refrigerant flows from the rapid inlet 121 through the air conditioning inlet pipe 11a. Refrigerant does not flow from 131 .

Refrigerant that has flowed in from the rapid inlet 121 flows along the direction in which the rapid upstream channel portion 120 extends, as shown in the refrigerant flow F1 shown in FIG. In this case, the flow direction of the coolant is changed by 30°. The refrigerant that has flowed into the downstream channel portion 140 flows along the direction in which the downstream channel portion 140 extends, and flows out from the refrigerant outlet port 143 to the compressor outlet pipe 11c.

In addition, in the heating mode and the cooling mode, the refrigerant flows into the connecting device 100 from the low inlet 131 through the cooling section inlet pipe 11b, but the refrigerant does not flow from the rapid inlet 121 . Refrigerant that has flowed in from the low inlet 131 flows along the direction in which the low upstream channel portion 130 extends, as shown in the refrigerant flow F2 shown in FIG. When doing so, the flow direction of the coolant is changed by 60°. The refrigerant that has flowed into the downstream channel portion 140 flows along the direction in which the downstream channel portion 140 extends, and flows out from the refrigerant outlet port 143 to the compressor outlet pipe 11c.

Also, in the cooling cooling mode, the refrigerant flows into the connection device 100 from the rapid inlet 121 through the air conditioning inlet pipe 11a and from the low inlet 131 through the cooling section inlet pipe 11b. Further, in the dehumidifying heating mode, when the second expansion valve 17b is throttled, the refrigerant flows into the connection device 100 through the air conditioning inflow pipe 11a from the rapid inflow inlet 121 and through the cooling unit inflow pipe 11b. and flows in from the low inlet 131 .

Refrigerant that has flowed in from the rapid inlet 121 flows along the direction in which the rapid upstream channel portion 120 extends, as indicated by a refrigerant flow F3 shown in FIG. The flow velocity vector of the refrigerant flowing along the direction in which rapid upstream flow path portion 120 extends has a downward flow velocity vector component in vertical direction DR1 and a leftward flow velocity vector component in horizontal direction DR3. The refrigerant flow velocity vector indicates the velocity vector of the refrigerant flow.

When the refrigerant flowing through the rapid upstream flow path portion 120 flows into the downstream flow path portion 140 from the rapid confluence port 122, the refrigerant flowing from the low confluence port 132 does not collide with the refrigerant flowing from the low confluence port 132, and the flow direction of the refrigerant changes by 30°. can be changed.

Refrigerant that has flowed in from the low inlet 131 flows along the direction in which the low upper flow path 130 extends, as indicated by a refrigerant flow F4 shown in FIG. The flow velocity vector of the refrigerant flowing along the direction in which the low upper flow path portion 130 extends has a downward flow velocity vector component in the vertical direction DR1 and a rightward flow velocity vector component in the horizontal direction DR3.

When the refrigerant flowing through the low upstream channel portion 130 flows into the downstream channel portion 140 from the low confluence port 132, it joins and collides with the coolant that has flowed into the downstream channel portion 140 from the rapid confluence port 122. , the flow of the refrigerant is changed by 60°. The refrigerant that has flowed into the downstream channel portion 140 from the rapid confluence port 122 and the low confluence port 132 flows along the direction in which the downstream channel portion 140 extends, and flows out from the refrigerant outlet port 143 to the compressor outlet pipe 11c. do. The flow velocity vector of the refrigerant that has flowed into the downstream channel portion 140 from the rapid confluence port 122 and the low confluence port 132 has a downward flow velocity vector component in the vertical direction DR1 and almost has flow velocity vector components in the other directions. No. Hereinafter, the operation mode of the refrigeration cycle device 10 in which the refrigerant collision occurs inside the housing 110 is also referred to as the refrigerant collision occurrence mode.

Here, regarding the pressure loss when the refrigerant collides in the refrigerant collision occurrence mode and the pressure loss when the refrigerant flow direction changes, the first comparative connection device 101 shown in FIG. 10 and the second comparative connection device 101 shown in FIG. A comparison with the connection device 102 for comparison will be described.

A first connection device 101 for comparison shown in FIG. 10 has a T-shaped outer shell protruding upward in the vertical direction DR1, and a coolant passage through which a coolant flows is formed therein.

Specifically, the first connecting device 101 for comparison includes a first upstream flow path portion 101a for comparison formed extending leftward from the surface on the right side in the left-right direction DR3, and a flow path portion 101a extending from the surface on the left side in the left-right direction DR3 to the right side. It has a second upstream flow path portion 101b for comparison formed extending toward. The left end portion of the first upstream flow path portion 101a for comparison in the left-right direction DR3 and the right end portion of the second upstream flow path portion 101b for comparison are located in the left-right direction DR3 of the first connection device 101 for comparison. are connected at approximately the center of the

The first comparison connection device 101 is formed by extending upward in the vertical direction DR1 from a portion where the first comparison upstream flow path portion 101a and the second comparison upstream flow path portion 101b are connected. It has a downstream flow path portion 101c. The comparison downstream channel portion 101c penetrates from a portion where the first comparison upstream channel portion 101a and the second comparison upstream channel portion 101b are connected to the upper surface of the first connection device 101 for comparison in the vertical direction DR1. It is formed by

The lower end portion of the comparison downstream flow path portion 101c in the vertical direction DR1 is connected to the comparison first upstream flow path portion 101a and the comparison second upstream flow path portion 101b. Further, the direction in which the first upstream channel portion 101a for comparison and the second upstream channel portion 101b for comparison extend is perpendicular to the direction in which the downstream channel portion 101c for comparison extends. That is, the first upstream flow path portion 101a for comparison and the second upstream flow path portion 101b for comparison are 90 degrees from the joining portion of the downstream flow path portion 101c for comparison toward the downstream side of the refrigerant flow of the downstream flow path portion 101c for comparison. °.

In the first comparison connection device 101, the air conditioning inflow pipe 11a is connected to the comparison first upstream flow path portion 101a, the cooling unit inflow pipe 11b is connected to the comparison second upstream flow path portion 101b, and the comparison downstream flow path is connected. A compressor outflow pipe 11c is connected to the path portion 101c.

In the first comparative connection device 101 configured as described above, when the refrigerant flows from the air conditioning inflow pipe 11a, the refrigerant flowing through the first comparative upstream flow path portion 101a is , from the right side to the left side in the horizontal direction DR3. On the other hand, when the refrigerant flows from the cooling section inflow pipe 11b, the refrigerant flowing through the second upstream flow path portion 101b for comparison flows from the left side to the right side in the left-right direction DR3, as indicated by the refrigerant flow F11 shown in FIG. flow.

In other words, the coolant flowing through the first upstream channel portion 101a for comparison and the coolant flowing through the second upstream channel portion 101b for comparison flow in opposite directions. Then, the coolant flowing through the comparison first upstream channel portion 101a and the comparison second upstream channel portion 101b collides when joining the comparison downstream channel portion 101c.

In addition, the flow direction of the refrigerant flowing through the first upstream flow path portion 101a for comparison and the second upstream flow path portion 101b for comparison is changed by 90° when joining the comparison downstream flow path portion 101c, as shown in FIG. As shown by the refrigerant flow F12, it flows upward in the vertical direction DR1.

Such collisions and changes in the flow direction of the coolant when the coolants merge cause pressure loss when the coolant flows through the first connection device 101 for comparison.

The second comparative connection device 102 shown in FIG. 11 has a rectangular parallelepiped outer shell, and a refrigerant passage through which a refrigerant flows is formed inside.

Specifically, the second connecting device 102 for comparison includes a first upstream flow path portion 102a for comparison formed from the surface on the right side in the left-right direction DR3 toward the left side, and a front side from the surface on the rear side in the front-rear direction DR2. It has a comparison second upstream flow path portion 102b that is formed facing the flow path. The left end portion of the first upstream flow path portion 102a for comparison in the left-right direction DR3 and the front end portion of the second upstream flow path portion 102b for comparison in the front-rear direction DR2 and substantially the center in the front-rear direction DR2.

The second connection device 102 for comparison is formed to extend downward in the vertical direction DR1 from a portion where the first upstream flow path portion 102a for comparison and the second upstream flow path portion 102b for comparison are connected. It has a downstream channel portion 102c for comparison. The downstream channel portion 102c for comparison extends from the portion where the first upstream channel portion 102a for comparison and the second upstream channel portion 102b for comparison are connected to the lower side of the second connection device 102 for comparison in the vertical direction DR1. It is formed penetrating to the surface.

The comparison downstream channel portion 102c is connected to the comparison first upstream channel portion 102a and the comparison second upstream channel portion 102b at the upper end in the vertical direction DR1. Further, the direction in which the first upstream channel portion 102a for comparison and the second upstream channel portion 102b for comparison extend is perpendicular to the direction in which the downstream channel portion 102c for comparison extends. That is, the first upstream flow path portion 102a for comparison and the second upstream flow path portion 102b for comparison are arranged in a direction toward the downstream side of the refrigerant flow of the downstream flow path portion 102c for comparison from the confluence portion of the downstream flow path portion 102c for comparison. is offset by 90° with respect to .

In the second comparative connecting device 102, the air conditioning inflow pipe 11a is connected to the comparative first upstream flow path portion 102a, the cooling unit inflow pipe 11b is connected to the comparative second upstream flow path portion 102b, and the comparison downstream A compressor outflow pipe 11c is connected to the side passage portion 102c.

In the second connection device 102 for comparison configured as described above, when the refrigerant flows from the air-conditioning inflow pipe 11a, as shown in the refrigerant flow F20 in FIG. It flows from the right side to the left side in the horizontal direction DR3. On the other hand, when the refrigerant flows in from the cooling section inflow pipe 11b, the refrigerant flowing through the comparison second upstream flow path portion 102b flows from the rear side to the front side in the front-rear direction DR2, as indicated by the refrigerant flow F21 in FIG. flow.

Then, the coolant that has flowed into the comparison first upstream channel portion 102a and the comparison second upstream channel portion 102b collides when joining the comparison downstream channel portion 102c.

Further, the flow direction of the refrigerant flowing through the comparison first upstream channel portion 102a and the comparison second upstream channel portion 102b is changed by 90° when joining the comparison downstream channel portion 101c, as shown in FIG. As shown by the refrigerant flow F22, it flows downward in the vertical direction DR1.

Such collisions and changes in the flow direction of the coolants when they join together cause pressure loss when the coolant flows through the second connection device 102 for comparison.

The pressure loss caused by the collision of the refrigerants increases as the number of flow velocity vector components in directions opposite to each other increases when the flow velocity vectors of the respective refrigerants before collision are vector-decomposed into the vertical direction DR1, the front-rear direction DR2, and the horizontal direction DR3. . On the other hand, when the flow velocity vector of each refrigerant before collision is vector-decomposed into the vertical direction DR1, the front-rear direction DR2, and the left-right direction DR3, the pressure loss becomes smaller as more flow velocity vector components in the same direction are included. Become.

Here, in the first comparative connection device 101 and the second comparative connection device 102, the refrigerant passage connected to the air conditioning inflow pipe 11a and the cooling section inflow pipe 11b is replaced with the upstream refrigerant passage and the compressor outflow pipe 11c. Let the refrigerant passage to which is connected be a refrigerant passage on the downstream side.

The pressure loss when the flow direction of the refrigerant changes increases as the difference in the flow direction of the refrigerant flowing through the downstream refrigerant passage from the flow direction of the refrigerant flowing through the upstream refrigerant passage increases. In other words, the direction in which the upstream refrigerant passage extends when the direction from the point where the upstream refrigerant passage joins the downstream refrigerant passage to the downstream side of the refrigerant flow of the downstream refrigerant passage is taken as a reference direction. becomes larger as the distance from the reference direction increases.

In the first comparative connection device 101, the refrigerant flowing through the first upstream flow path portion 101a for comparison and the second upstream flow path portion 101b for comparison flow in opposite directions and collide with each other. Pressure loss tends to increase. In addition, in the first comparison connection device 101, when the refrigerant flowing through the comparison first upstream flow path portion 101a and the comparison second upstream flow path portion 101b joins the comparison downstream flow path portion 101c, the respective flow directions of the refrigerants are can be changed by 90°. Therefore, the pressure loss is likely to increase further.

On the other hand, in the second connection device 102 for comparison, the refrigerant flowing through the first upstream flow path portion 102a for comparison and the second upstream flow path portion 102b for comparison do not include flow velocity vectors in opposite directions. Therefore, the pressure loss caused by the collision is suppressed as compared with the first connection device 101 for comparison.

However, when the refrigerants flowing through the comparison first upstream flow path portion 102a and the comparison second upstream flow path portion 102b join the comparison downstream flow path portion 102c, the second connection device 102 for comparison causes the flow of the respective refrigerants. The flow direction is changed by 90°. Therefore, the pressure loss tends to increase.

By the way, in a so-called refrigerant pipe connection block that joins the refrigerant flowing from a plurality of refrigerant pipes and guides it to the refrigerant pipe on the downstream side of the refrigerant flow, from the viewpoint of ease of manufacture, when the refrigerant joins and collides, the refrigerant does not flow. A configuration in which the flow direction can be changed by 90° is likely to be adopted. However, collisions and changes in the flow direction of the refrigerant when the refrigerants merge become factors of pressure loss when the refrigerant flows inside the refrigerant pipe connection block.

In addition, in the vehicle air conditioner 1 mounted on the electric vehicle, high performance battery cooling is required from the viewpoint of extending the cruising distance and shortening the time of quick charging. is an issue. On the other hand, as a method for suppressing the pressure loss, there is a method of increasing the inner diameter of the refrigerant pipe connecting 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 causes an increase in the manufacturing cost of the entire refrigeration cycle apparatus 10 due to an increase in the cost of refrigerant piping. Therefore, there is a need for a refrigerant pipe connection block that can suppress pressure loss without increasing the inner diameter of the refrigerant pipe.

On the other hand, in the connection device 100 of the present embodiment, the steep upstream channel portion 120 extends from the first confluence portion 141 with a deviation of 30° from the predetermined confluence reference direction DRC. Further, in the connection device 100, the low upstream flow path portion 130 extends from the second confluence portion 142 by 60° with respect to the predetermined confluence reference direction DRC. Furthermore, the connection device 100 is provided at a position where the first junction 141 is upstream of the second junction 142 in the refrigerant flow.

In the connection device 100 formed in this way, the coolant does not flow into the downstream channel portion 140 in the downstream channel portion 140 on the upstream side of the coolant flow from the first confluence portion 141 . Therefore, in the first confluence portion 141, when the refrigerant flowing through the rapid upstream flow path portion 120 flows into the downstream flow path portion 140, the refrigerant flowing into the downstream flow path portion 140 is different from the rapid upstream flow path portion 120. It does not collide with the coolant that has flowed into the downstream channel portion 140 from a different channel portion.

Therefore, when the coolant flowing through the steep upstream channel portion 120 flows into the downstream channel portion 140, no pressure loss occurs due to collision.

In addition, when the refrigerant flowing through the low upstream flow path portion 130 flows into the downstream flow path portion 140, the refrigerant that has flowed into the downstream flow path portion 140 flows downstream from the steep upstream flow path portion 120 at the second confluence portion 142. It joins and collides with the coolant that has flowed into the channel portion 140 .

The flow velocity vector of the refrigerant flowing through the low upper flow path portion 130 immediately before it flows into the second confluence portion 142 has a downward flow velocity vector component in the vertical direction DR1 and a rightward flow velocity vector component in the horizontal direction DR3. On the other hand, the flow velocity vector of the refrigerant immediately before the refrigerant flowing from the rapid upstream flow path part 120 into the downstream flow path part 140 flows into the second junction part 142 has a downward flow velocity vector component in the vertical direction DR1. and have almost no velocity vector components in other directions.

Thus, the flow velocity vector of the refrigerant flowing from the low upstream flow path portion 130 into the second confluence portion 142 conflicts with the flow velocity vector of the refrigerant flowing upstream of the second confluence portion 142 in the downstream flow path portion 140 . Does not include directional velocity vectors. Therefore, the pressure loss caused by the collision when the refrigerants join is suppressed compared to the first connection device 101 for comparison.

Further, the coolant flowing from the steep upstream channel portion 120 into the downstream channel portion 140 is changed in its flow direction by the first angle θ1 and flows downward in the vertical direction DR1. Specifically, the flow direction of the coolant flowing from the steep upstream channel portion 120 to the downstream channel portion 140 is changed by 30°.

That is, the amount of change in the flow direction of the coolant that changes when flowing from the steep upstream channel portion 120 to the downstream channel portion 140 is 30°. The amount of change is the amount of change in the flow direction of the refrigerant when the refrigerant passage on the upstream side joins the refrigerant passage on the downstream side in the first comparative connection device 101 and the second comparative connection device 102. less than 90°.

Then, the refrigerant flowing from the low upstream flow path portion 130 into the downstream flow path portion 140 changes its flow direction by the second angle θ2, joins the refrigerant flowing from the steep upstream flow path portion 120, and flows in the vertical direction DR1. flow toward the bottom of the Specifically, the flow direction of the coolant flowing from the low upstream channel portion 130 to the downstream channel portion 140 is changed by 60°.

In other words, the amount of change in the flow direction of the coolant when flowing from the low upstream channel portion 130 to the downstream channel portion 140 is 60°. The amount of change is 90°, which is the amount of change in the flow direction of the refrigerant when it joins the downstream refrigerant passage from the upstream refrigerant passage in the first comparative connection device 101 and the second comparative connection device 102. less than

Therefore, the pressure loss when the refrigerant flow direction changes in the present embodiment is similar to the pressure loss when the refrigerant flow direction changes in the first comparative connection device 101 and the second comparative connection device 102. suppressed in comparison.

As described above, in the connection device 100 of the present embodiment, the steep upstream channel portion 120 extends with a deviation of 30°, which is the first angle θ1, with respect to the predetermined confluence reference direction DRC. Further, the low upstream channel portion 130 extends with a deviation of 60°, which is the second angle θ2, with respect to the predetermined confluence reference direction DRC. Therefore, when the refrigerant flows from the rapid upstream flow path portion 120 and the low upstream flow path portion 130 to the downstream flow path portion 140, the pressure loss when the flow direction of the refrigerant changes can be suppressed.

(1) In the above embodiment, both the steep upstream channel portion 120 and the low upstream channel portion 130 extend at an angle larger than 0° and smaller than 90° with respect to the predetermined confluence reference direction DRC. Therefore, one of the steep upstream channel portion 120 and the low upstream channel portion 130 extends at an angle larger than 0° and smaller than 90° with respect to the predetermined confluence reference direction DRC, and the other extends with respect to the predetermined merge reference direction DRC. Pressure loss can be suppressed more than the configuration in which the extension is shifted by 90°.

(2) In the above-described embodiment, the downstream flow path portion 140 has an inner diameter on the downstream side of the refrigerant flow of the first confluence portion 141 that is larger than the inner diameter of the steep upstream flow path portion 120 and is larger than the second confluence portion 142. The inner diameter on the downstream side of the refrigerant flow is larger than the inner diameter of the low upstream flow path portion 130 .

Therefore, the speed of the refrigerant flowing through the downstream channel portion 140 is less than or equal to the inner diameter of the rapid upstream channel portion 120 at the downstream side of the refrigerant flow from the first merging portion 141, and the refrigerant flow rate is higher than that at the second merging portion 142. Compared to the case where the downstream side is formed with a size equal to or less than the inner diameter of the low upstream channel portion 130, the speed is slower. Therefore, compared to the case where the inner diameter of the downstream channel portion 140 is equal to or less than the inner diameters of the steep upstream channel portion 120 and the low upstream channel portion 130, when the coolant flows through the downstream channel portion 140, It is possible to suppress the pressure loss that occurs.

(3) In the above-described embodiment, the connecting device 100 has the air conditioning inflow pipe 11a connected to the rapid upstream channel portion 120, the cooling portion inflow pipe 11b connected to the low upstream channel portion 130, and the downstream channel A compressor outflow pipe 11 c is connected to the portion 140 . Further, the direction in which the steep upstream channel portion 120 extends with respect to the predetermined confluence reference direction DRC is smaller than the direction in which the low upstream channel portion 130 extends with respect to the predetermined merge reference direction DRC. That is, the first angle θ1 is smaller than the second angle θ2.

Here, in the vehicle air conditioner 1 mounted on the electric vehicle, air conditioning in the vehicle interior is relatively emphasized rather than cooling the battery 60 . Therefore, in the refrigeration cycle device 10 when operating in the refrigerant collision occurrence mode, it is necessary to flow more refrigerant through the air conditioning inflow pipe 11a than through the cooling portion inflow pipe 11b. In this case, more refrigerant flows into the connection device 100 from the steep upstream flow path portion 120 than from the low upstream flow path portion 130 .

Therefore, the pressure loss generated when joining the downstream channel portion 140 is greater than the pressure loss generated when joining from the low upstream channel portion 130 . has a large effect on the pressure loss of the entire refrigeration cycle apparatus 10.

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 joining the downstream channel portion 140 is greater than that when joining the downstream channel portion 140 from the low upstream channel portion 130 . It is smaller when it merges with the path portion 140 . Therefore, the pressure loss when the flow direction of the refrigerant changes when joining the downstream channel portion 140 from the steep upstream channel portion 120 is It is possible to suppress the pressure loss when the flow direction of the refrigerant changes.

Therefore, when more refrigerant flows in the air conditioning inflow pipe 11a than in the cooling part inflow pipe 11b, the pressure loss of the entire refrigeration cycle device 10 can be suppressed as compared to the case without such a configuration.

(4) In the above-described embodiment, the most downstream side of the refrigerant flow of the downstream flow passage portion 140 is vertically lower than the most upstream side of the refrigerant flow of the steep upstream flow passage portion 120 and the most upstream side of the refrigerant flow of the low upstream flow passage portion 130. placed in position. In other words, coolant outlet 143 is positioned more vertically than rapid inlet 121 and low inlet 131 .

Here, as described above, when the second expansion valve 17b in the dehumidification/heating mode of the vehicle air conditioner 1 operates in the throttling state and the cooling mode, the refrigerant flows into the connection device 100 from the rapid flow inlet 121. On the other hand, it does not flow from the low inlet 131 . Also, when the vehicle air conditioner 1 operates in the heating mode and the cooling mode, refrigerant flows into the connecting device 100 from the low inlet 131 but does not flow from the rapid inlet 121 .

In this way, when the refrigerant flows only from either the rapid inlet 121 or the low inlet 131, the oil that has flowed into the housing 110 together with the refrigerant flows inside the housing 110. There is a risk that the coolant will flow backwards and flow out from the other inflow port to which the coolant does not flow.

In the above-described embodiment, the refrigerant outlet 143 is positioned vertically below the rapid inlet 121 and the low inlet 131, so that the oil flowing into the housing 110 together with the refrigerant flows vertically downward. It becomes easy to flow towards. Therefore, even in an operation mode in which the refrigerant flows only from one inlet, it is possible to prevent the oil that has flowed in from flowing backward through the housing 110 and flowing out from the inlet on the side to which the refrigerant does not flow.

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

Therefore, when the vehicle air conditioner 1 stops operating, the oil that has flowed out together with the refrigerant from the refrigerant outflow port 143 flows backward inside the housing 110 and flows out from the rapid flow inlet 121 and the low flow inlet 131. can be suppressed.

(5) In the above embodiment, the inner diameter of the rapid upstream channel portion 120 is formed to correspond to the most downstream portion of the refrigerant flow of the air conditioning inflow pipe 11a, and the inner diameter of the low upstream channel portion 130 is formed to correspond to the cooling portion inflow pipe 11b. is formed in a size corresponding to the most downstream portion of the refrigerant flow. In addition, the inner diameter of the downstream channel portion 140 is larger than the inner diameter of the steep upstream channel portion 120 and the inner diameter of the low upstream channel portion 130, and is formed in a size corresponding to the most upstream portion of the refrigerant flow of the compressor outflow pipe 11c. there is

For this reason, measures such as installing a refrigerant pipe conversion member for connecting the air conditioning inflow pipe 11a to the rapid inlet 121 and installing a refrigerant pipe conversion member for connecting the cooling unit inflow pipe 11b to the low inlet 131 are available. becomes unnecessary. In addition, it is not necessary to attach a refrigerant pipe conversion member for connecting the compressor outflow pipe 11c to the refrigerant outflow port 143, or the like.

Therefore, it is possible to suppress an increase in the manufacturing cost while suppressing the pressure loss that occurs when the coolant flows through the downstream channel portion 140 .

(6) In the above-described embodiment, the first merging portion 141 and the second merging portion 142 are provided at different positions in the downstream channel portion 140 . Specifically, the first merging portion 141 is positioned upstream of the second merging portion 142 in the refrigerant flow. Therefore, when the rapid upstream flow path portion 120 and the low upstream flow path portion 130 merge at the downstream flow path portion 140, the position at which the rapid upstream flow path portion 120 merges and the position at which the low upstream flow path portion 130 merge are at different positions. can be

Therefore, when the refrigerant that merges from the steep upstream flow path portion 120 connected to the first confluence portion 141 merges with the downstream flow path portion 140, the refrigerant that joins the downstream flow path portion 140 from the low upstream flow path portion 130 Collisions can be avoided. Therefore, the pressure loss due to the collision when the refrigerant joins in the downstream flow path section 140 can be suppressed as compared to the case without such a configuration.

(7) In the above-described embodiment, in the downstream channel portion 140 , the first junction portion 141 is provided at a position upstream of the second junction portion 142 in the refrigerant flow.

By the way, in the downstream flow path portion 140, if there is a refrigerant passage that joins with a portion in the middle of the flow path of the downstream flow path portion 140, the refrigerant flowing through the downstream flow path portion 140 causes the refrigerant flowing through the merged refrigerant passage to A pulling force to the downstream flow path portion 140 is generated. The force of drawing into the downstream flow passage portion 140 increases as the flow rate of the refrigerant flowing through the downstream flow passage portion 140 increases.

Further, as described above, in the refrigerant collision occurrence mode of the vehicle air conditioner 1, which is often used for air conditioning the vehicle interior rather than for cooling the battery 60, the connection device 100 includes the low upstream flow path portion 130. A larger amount of refrigerant flows from the steep upstream channel portion 120 than from the .

In the above-described embodiment, the first merging portion 141 is provided at a position upstream of the second merging portion 142 in the flow of the refrigerant. The refrigerant flowing through the low upper flow path portion 130 joins. Therefore, due to the flow of the refrigerant flowing from the rapid upstream flow path portion 120 through which more refrigerant than the low upstream flow path portion 130 flows, the refrigerant flowing through the low upstream flow path portion 130 joining from the middle of the refrigerant path is prevented from flowing into the downstream flow path portion. A pulling force to 140 can be generated.

Therefore, compared to the configuration in which the first merging portion 141 is provided downstream of the second merging portion 142 in the flow of the refrigerant, the force for drawing the refrigerant into the downstream flow path portion 140 can be increased, so that the flow direction of the refrigerant changes. It is possible to suppress the pressure loss when
(First Modification of First Embodiment)
In the first embodiment described above, an example in which the steep upstream flow path portion 120 and the low upstream flow path portion 130 are formed such that the first angle θ1 is smaller than the second angle θ2 has been described, but the present invention is not limited to this. For example, the steep upstream flow path portion 120 and the low upstream flow path portion 130 may be configured such that the first angle θ1 is greater than the second angle θ2 as long as the angle is greater than 0° and less than 90°. . Further, the steep upstream flow path portion 120 and the low upstream flow path portion 130 are configured such that the first angle θ1 and the second angle θ2 are the same as long as the angle is greater than 0° and less than 90°. good too.
(Second Modification of First Embodiment)
In the above-described first embodiment, an example in which the first confluence portion 141 is provided upstream of the second confluence portion 142 in the flow of the refrigerant in the downstream channel portion 140 has been described, but the present invention is not limited to this. For example, the first merging portion 141 may be provided at a position on the downstream side of the flow of the refrigerant from the second merging portion 142 in the downstream channel portion 140 . Alternatively, the steep upstream channel portion 120 and the low upstream channel portion 130 may be configured to merge with the downstream channel portion 140 at mutually equal positions.

(Second embodiment)
Next, a second embodiment will be described with reference to FIGS. 12 to 14. FIG. This embodiment differs from the first embodiment in the outer diameter of the air conditioning inflow pipe 11a, the shape of the housing 210, and the shape of the refrigerant passage formed inside the housing 210. FIG. In this embodiment, portions different from the first embodiment will be mainly described, and descriptions of portions similar to the first embodiment may be omitted.

A refrigerant pipe having an outer diameter of 19.05 mm from the inlet side to the outlet side is adopted as the air conditioning inflow pipe 11a of the present embodiment. The outer diameter of the air conditioning inflow pipe 11a is larger than the outer diameter of the cooling section inflow pipe 11b and is the same as the outer diameter of the compressor outflow pipe 11c. That is, the air-conditioning inflow pipe 11a of this embodiment employs a refrigerant pipe having a larger outer diameter than the air-conditioning inflow pipe 11a of the first embodiment.

12 and 13, the connection device 200 has a housing 210, and in the interior of the housing 210, a serial upstream channel portion 220, an inclined upstream channel portion 230, and a serial downstream channel portion, which are refrigerant passages. 250 are formed.

The housing 210 of this embodiment is formed in a cubic shape in which the size in the vertical direction DR1 is larger than the size in the front-rear direction DR2 and the size in the left-right direction DR3. Housing 210 has an upper surface portion 211 provided on the upper side in vertical direction DR1 and a lower surface portion 212 provided on the lower side in vertical direction DR1. Further, the housing 210 has a right surface portion 213 extending from the right end portion of the upper surface portion 211 in the horizontal direction DR3 toward the lower side in the vertical direction DR1 to the right end portion of the lower surface portion 212 in the horizontal direction DR3. Further, the housing 210 has a left surface portion 214 extending from the left end portion of the upper surface portion 211 in the horizontal direction DR3 toward the lower side in the vertical direction DR1 to the left end portion of the lower surface portion 212 in the horizontal direction DR3.

As shown in FIG. 12 , a serial upstream passage portion 220 extending from the surface of the upper surface portion 211 toward the lower surface portion 212 is formed as a refrigerant passage inside the housing 210 . In addition, an inclined upstream channel portion 230 is formed inside the housing 210 so as to extend from the surface of the right surface portion 213 toward the left surface portion 214 at an angle without passing through the left surface portion 214 . Further, inside the housing 210, a series downstream flow path portion 250 is formed that extends upward in the vertical direction DR1 from the surface of the bottom surface portion 212. As shown in FIG.

Serial upstream flow path portion 220 extends linearly along vertical direction DR1 from approximately the center of the surface of upper surface portion 211 toward approximately the center of lower surface portion 212 . In addition, the serial upstream channel portion 220 is positioned on the end opposite to the side positioned on the surface of the upper surface portion 211 among both ends, and on the surface of the lower surface portion 212 among both ends of the serial downstream channel portion 250 . The end opposite to the side to be connected is connected. Further, the serial upstream channel portion 220 is positioned on the end opposite to the surface of the upper surface portion 211 among both ends, and on the surface of the right surface portion 213 among both ends of the inclined upstream channel portion 230 . The end opposite to the side to be connected is connected.

Inclined upstream flow path portion 230 extends from a portion of the surface of right surface portion 213 above the center in vertical direction DR1 toward a portion below the center of left surface portion 214 in vertical direction DR1. In addition, the inclined upstream channel portion 230 is positioned on the surface of the lower surface portion 212 of both ends of the serial downstream channel portion 250 , at the end opposite to the side positioned on the surface of the right surface portion 213 . The end opposite to the side to be connected is connected. Further, the inclined upstream flow path portion 230 is positioned on the surface of the upper surface portion 211 of the both end portions of the serial upstream flow path portion 220 , at the end opposite to the side positioned on the surface of the right surface portion 213 . The end opposite to the side to be connected is connected.

That is, in the present embodiment, the serial upstream channel portion 220, the inclined upstream channel portion 230, and the serial downstream channel portion 250 are directly connected. Specifically, the most downstream portion of the refrigerant flow in the serial upstream passage portion 220 and the most downstream portion of the refrigerant flow in the inclined upstream passage portion 230 are directly connected at the most upstream portion of the refrigerant flow in the serial downstream passage portion 250 . Therefore, the refrigerant flowing from the upstream upstream flow path portion 220 to the downstream downstream flow path portion 250 and the refrigerant flowing from the inclined upstream flow path portion 230 to the downstream downstream flow path portion 250 directly join the downstream downstream flow path portion 250 . In this embodiment, the serial upstream channel portion 220 functions as a serial upstream channel portion, the inclined upstream channel portion 230 functions as an inclined upstream channel portion, and the serial downstream channel portion 250 functions as a downstream channel portion. do.

The serial upstream flow path portion 220 forms a refrigerant passage for guiding the refrigerant flowing out of the air conditioning inflow pipe 11a into the housing 210, and extends straight along the same direction as the serial downstream flow path portion 250 extends. extending in the shape of The serial upstream channel portion 220 has a serial inlet port 221 to which the air conditioning inlet pipe 11a is connected on the upstream side of the refrigerant flow, and a serial junction port 222 that communicates with the serial downstream channel portion 250 on the downstream side of the refrigerant flow. In addition, in FIG. 13, the series confluence port 222 is indicated by a dashed line for convenience of explanation. The direction in which the serial upstream channel portion 220 extends will be described later.

Further, the serial upstream flow path portion 220 is formed such that the fourth inner diameter φ4, which is the inner diameter of the serial upstream flow path portion 220, is slightly larger than the outer diameter of the air conditioning inflow pipe 11a. It is formed so that the air conditioning inflow pipe 11a can be inserted. Specifically, the inner diameter of the serial upstream channel portion 220 is formed slightly larger than the outer diameter of 19.05 mm of the air conditioning inflow pipe 11a.

The serial upstream channel portion 220 is formed so that the fourth inner diameter φ4 is equal from the serial inlet 221 to the serial confluence port 222 . The fourth inner diameter φ4 is the diameter of the cross-sectional shape in the direction perpendicular to the direction in which the serial upstream flow path portion 220 extends. The inner diameter of the serial upstream channel portion 220 is larger than the inner diameter of the inclined upstream channel portion 230 and the same size as the inner diameter of the serial downstream channel portion 250 .

The inclined upstream passage portion 230 forms a refrigerant passage for guiding the refrigerant flowing out of the cooling portion inflow pipe 11 b into the housing 210 . Inclined upstream channel portion 230 linearly extends in a direction different from the direction in which serial upstream channel portion 220 extends and the direction in which serial downstream channel portion 250 extends.

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

The inclined upstream channel portion 230 has a fifth inner diameter φ5, which is the inner diameter of the inclined upstream channel portion 230, slightly larger than the outer diameter of the cooling portion inflow pipe 11b. It is formed so that the inflow pipe 11b can be inserted. Specifically, the inner diameter of the inclined upstream channel portion 230 is formed slightly larger than the outer diameter of 15.88 mm of the cooling portion inflow pipe 11b.

The inclined upstream flow path portion 230 is formed such that the fifth inner diameter φ5 is uniform from the refrigerant flow upstream side to the refrigerant flow downstream side. The fifth inner diameter φ5 is the diameter of the cross-sectional shape in the direction orthogonal to the direction in which the inclined upstream flow path portion 230 extends.

The serial downstream channel portion 250 forms a coolant passage for causing the coolant, which has flowed into the housing 210 via the serial upstream channel portion 220 and the inclined upstream channel portion 230, to flow out of the housing 210. . Serial downstream flow path portion 250 linearly extends from substantially the center of the surface of lower surface portion 212 toward substantially the center of upper surface portion 211 along vertical direction DR1.

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

The serial downstream flow path portion 250 has a plurality of confluence portions 251 that join the refrigerant flowing through the serial upstream flow path portion 220 and the inclined upstream flow path portion 230 into the serial downstream flow path portion 250 on the upstream side of the refrigerant flow. In addition, the serial downstream flow path portion 250 has a serial outlet 253 to which the compressor outlet pipe 11c is connected on the most downstream side of the refrigerant flow.

Here, a straight line L4 passing through the center of the serial outlet 253 and along the direction in which the serial downstream flow section 250 extends intersects with a straight line L5 passing through the center of the serial inlet 221 and along the direction in which the serial upstream flow section 220 extends. Let the part where it joins is the multiple confluence part 251. As shown in FIG. A straight line L4 passing through the center of the serial outlet 253 and extending along the direction in which the serial downstream flow section 250 extends, and a straight line L6 passing through the center of the inclined inlet 231 and along the direction in which the inclined upstream flow section 230 extends. It is also the part where the

That is, in the present embodiment, in the serial downstream flow section 250, the position where the serial upstream flow section 220 joins and the position where the inclined upstream flow section 230 joins are provided at the same position. The plurality of confluence portions 251 is a portion into which the refrigerant flowing through the series upstream channel portion 220 and the inclined upstream channel portion 230 respectively flows. In this embodiment, the multiple confluence section 251 functions as a confluence section.

In addition, in the series downstream flow path portion 250, a series outlet 253, which is the most downstream side of the refrigerant flow, is provided below the series inflow port 221, which is the most upstream side of the refrigerant flow of the series upstream flow path portion 220, in the vertical direction DR1. there is In the serial downstream channel portion 250, the serial outlet 253, which is the most downstream side of the refrigerant flow, is provided below the inclined inlet port 231, which is the most upstream side of the refrigerant flow, of the inclined upstream channel portion 230 in the vertical direction DR1. there is In other words, the serial outlet 253 is positioned below the serial inlet 221 and the inclined inlet 231 in the vertical direction.

In addition, the serial downstream flow passage portion 250 is formed such that the sixth inner diameter φ6, which is the inner diameter of the serial downstream flow passage portion 250, is slightly larger than the outer diameter of the compressor outflow pipe 11c. Compressor outflow pipe 11c is formed to be insertable. Specifically, the inner diameter of the serial downstream passage portion 250 is slightly larger than the outer diameter of 19.05 mm of the compressor outflow pipe 11c.

The serial downstream channel portion 250 is formed such that the sixth inner diameter φ6 is equal from the multiple confluence portion 251 to the serial outlet 253 . Furthermore, the sixth inner diameter φ6 is formed equal to the fourth inner diameter φ4. On the other hand, the sixth inner diameter φ6 is formed larger than the fifth inner diameter φ5. That is, the serial downstream flow path portion 250 has an inner diameter downstream of the plurality of merging portions 251 in the refrigerant flow, which is equal to the inner diameter of the serial upstream flow path portion 220 and larger than the inner diameter of the inclined upstream flow path portion 230 .

In other words, in the series downstream flow path part 250, the flow path cross-sectional area of the cross section perpendicular to the refrigerant flow direction is the direction orthogonal to the refrigerant flow direction in the series upstream flow path part 220 on the refrigerant flow downstream side of the multiple junction part 251. is equal to the channel cross-sectional area of the cross-section of In addition, in the serial downstream flow path portion 250, the flow path cross-sectional area of the cross section perpendicular to the refrigerant flow direction is the cross section of the cross section perpendicular to the refrigerant flow direction in the inclined upstream flow path portion 230 on the refrigerant flow downstream side of the multiple merging portion 251. larger than the cross-sectional area of the flow path.

In this embodiment, the ratio of the inner diameter of the serial downstream flow section 250 to the inner diameter of the serial upstream flow section 220 is one. In contrast, the ratio of the inner diameter of the serial downstream flow section 250 to the inner diameter of the inclined upstream flow section 230 is 1.20.

Subsequently, the details of the directions in which the serial upstream channel portion 220 and the inclined upstream channel portion 230 extend will be described using a predetermined confluence reference direction DRC. Here, the direction along the vertical direction DR1 and extending from the plurality of confluence portions 251 toward the downstream side of the refrigerant flow of the series downstream flow path portion 250 is defined as the downstream direction, and the direction opposite to the downstream direction is the predetermined confluence reference. Let the direction be DRC. The predetermined confluence reference direction DRC is an upward direction along the vertical direction DR1 with the plurality of confluence portions 251 as a reference.

As shown above, the serial upstream channel portion 220 extends linearly in the same direction as the serial downstream channel portion 250 extends. Therefore, the serial upstream channel portion 220 extends along the predetermined confluence reference direction DRC. Therefore, the angle formed by the predetermined confluence reference direction DRC and the direction in which the serial upstream channel portion 220 extends is 0° with the plurality of confluence portions 251 as the center. The direction in which serial upstream flow path portion 220 extends does not include left-right direction DR3 and front-rear direction DR2.

On the other hand, the inclined upstream flow path portion 230 extends by a third angle θ3 greater than 0° and less than 90° with respect to the predetermined confluence reference direction DRC, with the multiple confluence portion 251 as a reference. Here, the angle extending from the plurality of merging portions 251 deviated from the predetermined merging reference direction DRC means that the upper side of the vertical direction DR1 is 0° and the clockwise direction is the positive direction in the sectional view shown in FIG. is the angle to The third angle θ3 is an angle formed by the predetermined confluence reference direction DRC and the direction in which the inclined upstream channel portion 230 extends, with the plurality of confluence portions 251 being the center.

In this embodiment, the inclined upstream flow path portion 230 extends so that the third angle θ3 is 45°. Thus, the direction in which the inclined upstream flow path portion 230 of the present embodiment extends includes the horizontal direction DR3 and the vertical direction DR1, but does not include the front-rear direction DR2. Note that the third angle θ3 may be an angle larger than 45° or smaller than 45° as long as it is within a range of greater than 0° and less than 90°.

Next, the refrigerant flow and pressure loss when the refrigerant flows through the connection device 200 of the present embodiment when the refrigeration cycle device 10 is operated in the refrigerant collision occurrence mode will be described with reference to FIG. 14 . In the present embodiment, the refrigerant flowing through the series upstream flow path portion 220 flows downward in the vertical direction DR1 along the direction in which the series upstream flow path portion 220 extends, as indicated by refrigerant flow F5 in FIG. 14 . The flow velocity vector of the refrigerant flowing along the direction in which serial upstream flow path portion 220 extends has a downward flow velocity vector component in vertical direction DR1 and does not have flow velocity vector components in other directions. That is, the flow velocity vector of the refrigerant flowing from the series junction port 222 into the serial downstream flow path portion 250 has a downward flow velocity vector component in the vertical direction DR1 and almost no flow velocity vector components in other directions.

In addition, serial upstream channel portion 220 is provided on the same straight line as serial downstream channel portion 250, and is formed to extend along vertical direction DR1, which is the direction in which serial downstream channel portion 250 extends. Therefore, in the present embodiment, the flow direction of the refrigerant that flows into the series downstream flow path portion 250 from the series junction port 222 is not substantially changed when flowing into the series downstream flow path portion 250 .

Refrigerant flowing through the inclined upstream flow path portion 230 flows along the direction in which the inclined upstream flow path portion 230 extends, as indicated by refrigerant flow F6 in FIG. The flow velocity vector of the refrigerant flowing along the direction in which the inclined upstream flow path portion 230 extends has a downward flow velocity vector component in the vertical direction DR1 and a leftward flow velocity vector component in the lateral direction DR3, and a flow velocity vector component in the longitudinal direction DR2. does not have That is, the flow velocity vector of the refrigerant flowing from the inclined confluence port 232 into the serial downstream flow path portion 250 has a downward flow velocity vector component in the vertical direction DR1 and a leftward flow velocity vector component in the horizontal direction DR3. It does not have a flow velocity vector for DR2.

Further, in the serial downstream flow path portion 250, the position where the serial upstream flow channel portion 220 joins and the position where the inclined upstream flow channel portion 230 joins are provided at the same position. Therefore, in the connection device 200 of the present embodiment, when the refrigerant flowing through the serial upstream flow path portion 220 flows from the series junction port 222 into the serial downstream flow path portion 250, it flows from the inclined upstream flow path portion 230 into the serial downstream flow channel portion 250. It is configured such that it collides with the refrigerant to be applied.

Refrigerant flowing into the serial downstream flow passage portion 250 from the inclined confluence port 232 joins and collides with the refrigerant flowing into the serial downstream flow passage portion 250 from the serial confluence port 222, and collides with the refrigerant flowing into the serial downstream flow passage portion 250 at an angle larger than 0° and smaller than 90°. The flow direction of the coolant is changed by a certain third angle θ3. In the present embodiment, the flow direction of the refrigerant that has flowed into the series downstream flow section 250 from the inclined confluence port 232 is changed by 45°.

As described above, in the connection device 200 of the present 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. Other configurations and operations of the connection device 200 are the same as in the first embodiment. According to this, an effect similar to that of the first embodiment can be obtained.

In addition, serial upstream channel portion 220 is provided on the same straight line as serial downstream channel portion 250, and is formed to extend along vertical direction DR1, which is the direction in which serial downstream channel portion 250 extends. Therefore, the refrigerant that has flowed into the serial downstream flow path portion 250 from the series confluence port 222 flows downward in the vertical direction DR1 without substantially changing the flow direction of the refrigerant.

Therefore, in the connection device 200 of the present embodiment, the pressure loss when the refrigerant flow direction changes can be suppressed compared to the configuration in which the series upstream flow path portion 220 extends with a deviation from the predetermined confluence reference direction DRC. can be done.

In addition, the refrigerant flowing from the inclined confluence port 232 into the serial downstream flow passage portion 250 joins and collides with the refrigerant flowing into the serial downstream flow passage portion 250 from the serial confluence port 222, and the flow direction of the refrigerant is changed by 45°. . Then, the refrigerant that has flowed into the series downstream flow path portion 250 from the inclined confluence port 232 flows downward in the vertical direction DR1 together with the refrigerant that has flowed in from the series confluence port 222 .

Therefore, in the connection device 200 of the present embodiment, compared to the case where the inclined upstream flow path portion 230 extends with a deviation of 90° from the predetermined confluence reference direction DRC, the amount of change in the refrigerant flow direction can be reduced. Therefore, it is possible to suppress the pressure loss when the flow direction of the refrigerant changes.

In addition, in the connection device 200 of the present embodiment, the flow velocity vector of the refrigerant flowing from the serial upstream passage portion 220 into the multiple junction portions 251 conflicts with the flow velocity vector of the refrigerant flowing into the multiple junction portions 251 from the inclined upstream passage portion 230. Does not include directional velocity vectors. Therefore, the pressure loss due to the collision when the refrigerants join can be suppressed as compared with the case without such a configuration.

(1) In the above-described embodiment, the serial downstream flow path portion 250 has an inner diameter larger than that of the inclined upstream flow path portion 230 on the downstream side of the plurality of confluence portions 251 .

Therefore, in the series downstream flow path portion 250, the speed of the refrigerant flowing downstream of the plurality of junctions 251 in the refrigerant flow is slow in comparison. Therefore, compared to the case where the inner diameter of the serial downstream flow path portion 250 is equal to or less than the inner diameter of the inclined upstream flow path portion 230, the pressure loss generated when the refrigerant flows through the serial downstream flow path portion 250 can be suppressed. can be done.

(2) In the above-described embodiment, the connection device 200 has the air conditioning inflow pipe 11a connected to the serial upstream channel portion 220, the cooling portion inflow pipe 11b connected to the inclined upstream channel portion 230, and the serial downstream channel portion. 250 is connected to the compressor outflow pipe 11c.

Here, as described above, when the vehicle air conditioner 1, which is often used for air conditioning the vehicle interior rather than for cooling the battery 60, is operated in the refrigerant collision occurrence mode, the connection device 200 has an inclined More refrigerant flows into the serial upstream channel portion 220 than into the upstream channel portion 230 .

In the above embodiment, the air-conditioning inflow pipe 11a is connected to the serial upstream channel portion 220 in which the flow direction of the refrigerant does not substantially change when joining the serial downstream channel portion 250 . Therefore, compared to the configuration in which the air-conditioning inflow pipe 11a is connected to the inclined upstream channel portion 230, the refrigerant flows in the serial downstream channel portion 250 from the serial upstream channel portion 220 and the inclined upstream channel portion 230. It is possible to suppress the pressure loss when changing.

Therefore, when more refrigerant flows in the air conditioning inflow pipe 11a than in the cooling part inflow pipe 11b, the pressure loss of the entire refrigeration cycle device 10 can be suppressed compared to the case where this configuration is not provided.

(Third embodiment)
Next, a third embodiment will be described with reference to FIGS. 15 to 18. FIG. In this embodiment, as shown in FIG. 15, a rear seat air conditioning unit 80 is added to the refrigeration cycle apparatus 10 as compared with the second embodiment. Further, in this embodiment, along 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, portions different from the second embodiment will be mainly described, and descriptions of portions similar to the second embodiment may be omitted.

First, the rear seat air conditioning unit 80 will be described. The rear-seat air-conditioning unit 80 is for blowing the blown air whose temperature has been adjusted by the refrigerating cycle device 10 into the space in the passenger compartment where mainly the rear seats are provided. On the other hand, the indoor air-conditioning unit 50 blows out the blown air whose temperature has been adjusted by the refrigerating cycle device 10 into the space in the passenger compartment where the driver's seat is mainly provided. The first target space in this embodiment is the space in which the driver's seat is provided. Also, the second target space in this embodiment is a space different from the space in which the driver's seat is provided. Specifically, the second target space is a space in which the rear seats are provided.

As shown in FIG. 15, the rear seat air conditioning unit 80 has a rear seat evaporator 14b and a rear seat heater core 88 arranged in an air passage formed in a rear seat air conditioning case 81 forming the outer shell thereof. . Further, in the indoor air conditioning unit 50, a front seat evaporator 14a is arranged in an air conditioning case 51 instead of the indoor evaporator 14. As shown in FIG.

The front seat evaporator 14a and the rear seat evaporator 14b correspond to the indoor evaporator 14, and are cooling heat exchangers that cool the air blown into the passenger compartment. The rear seat heater core 88 corresponds to the heater core 35, and is a heat exchanger for heating that heats air blown into the passenger compartment. 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.

The rear seat air conditioning case 81 accommodates 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 cold air bypass passage 85 is provided for bypassing the rear seat heater core 88 and allowing the blown air after passing through the rear seat evaporator 14b to flow. Further, inside the rear seat air conditioning case 81, a rear seat mixing space 87 is arranged on the downstream side of the rear seat cool air bypass passage 85 in the blown air flow.

An opening hole for blowing air to the space where the rear seat is provided is arranged on the downstream side of the rear seat air-conditioning case 81 in the blown air flow. This opening hole is connected to a rear seat air outlet (not shown) provided on the ceiling of the passenger compartment and serving as an air outlet for blowing conditioned air toward passengers in the rear seats.

The rear seat air mix door 86 adjusts the air volume ratio between the air volume passing through the rear seat heater core 88 and the air volume passing through the rear seat cold air bypass passage 85, thereby increasing the temperature of the air blown out from the rear seat outlet. adjusted.

The rear seat inside/outside air switching device 82, the rear seat blower 83, the rear seat evaporator temperature sensor 84, and the rear seat air mix door 86 are connected to the inside/outside air switching device 52, the blower 53, the evaporator temperature sensor 54, and the air mix door 56, respectively. Since the configurations and functions are the same, detailed description is omitted.

In this embodiment, the refrigeration cycle device 10 has a refrigerant passage that circulates the refrigerant to the rear seat air conditioning unit 80 . The high temperature side heat medium circuit 30 also has a high temperature side heat medium passage for circulating the high temperature side heat medium to the rear seat air conditioning unit 80 .

Specifically, as shown in FIG. 15, the refrigerant passage connected to one outlet of the refrigerant branch portion 18 is branched midway. The inlet side of the first expansion valve 17a is connected to one side of the branched refrigerant passage. The inlet side of the third expansion valve 17c is connected to the branched refrigerant passage on the other side.

The refrigerant inlet side of the front seat evaporator 14a is connected to the outlet of the first expansion valve 17a. A front air conditioning inflow pipe 11d for guiding the refrigerant flowing out of the front evaporator 14a to the connecting device 200 is connected to the refrigerant outlet side of the front evaporator 14a. The front air conditioning inflow pipe 11d is inserted into a series inflow port 221 of the connection device 200, which will be described later, on the downstream side of the refrigerant flow.

The third expansion valve 17c reduces the pressure of the refrigerant flowing out of the refrigerant passage of the water-refrigerant heat exchanger 13 in the operating mode for mainly cooling the space in which the rear seat is provided, and the flow rate of the refrigerant flowing out to the downstream side. This is the rear seat decompression unit that adjusts the The basic configuration of the third expansion valve 17c is similar to that of the first expansion valve 17a and the second expansion valve 17b. The refrigerant inlet side of the rear seat evaporator 14b is connected to the outlet of the third expansion valve 17c. A rear seat inflow pipe 11e for guiding the refrigerant flowing out of the rear seat evaporator 14b to the connection device 200 is connected to the refrigerant outlet side of the rear seat evaporator 14b. The downstream side of the refrigerant flow of the rear seat inflow pipe 11e is inserted into a second inclined inflow port 241 of the connection device 200, which will be described later.

In this embodiment, the front seat air conditioning inflow pipe 11d functions as a first air conditioning inflow pipe, and the rear seat inflow pipe 11e functions as a second air conditioning inflow pipe. The front air conditioning inflow pipe 11d corresponds to the air conditioning inflow pipe 11a of the second embodiment.

The rear seat inflow pipe 11e of the present embodiment has an outer diameter smaller than that of the front air conditioning inflow pipe 11d and the compressor outflow pipe 11c, and has the same outer diameter as that of the cooling part inflow pipe 11b. A refrigerant pipe having an outer diameter of 15.88 mm is adopted.

Further, a fourth refrigerant temperature sensor 19g for detecting the temperature of the refrigerant flowing out of the rear seat evaporator 14b and a fourth refrigerant temperature sensor 19g for detecting the pressure of the refrigerant flowing out from the rear seat evaporator 14b are connected to the rear seat inflow pipe 11e. A pressure sensor 19h is provided. Further, the rear seat inflow pipe 11e is provided with a rear seat evaporation pressure control valve 15a for adjusting the pressure of the refrigerant flowing out from the rear seat evaporator 14b.

The fourth refrigerant temperature sensor 19g, the fourth refrigerant pressure sensor 19h, and the rear seat evaporating pressure regulating valve 15a have the same configurations and functions as the second refrigerant temperature sensor 19b, the second refrigerant pressure sensor 19e, and the evaporating pressure regulating valve 15, respectively. Therefore, detailed description is omitted.

16 and 17, in the connection device 200 of the present embodiment, the refrigerant flowing out from the rear seat evaporator 14b and flowing through the rear seat inflow pipe 11e flows into the housing 210. A two-sloped upstream channel section 240 has been added.

Further, in the high temperature side heat medium circuit 30, as shown in FIG. 15, the high temperature side heat medium passage connected to the other outflow port of the high temperature side flow control valve 33 is branched in the middle. The heat medium inlet side of the heater core 35 is connected to one of the branched high temperature side heat medium passages. 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 branched side.

A third high-temperature-side heat medium temperature sensor 37c that detects the temperature of the high-temperature-side heat medium before flowing into the rear seat heater core 88 is provided in the other branched high-temperature-side heat medium passage. The third high-temperature-side heat medium temperature sensor 37c sends a detection signal to the control device 70 according to the temperature of the high-temperature-side heat medium that has flowed out of the high-temperature-side flow control valve 33 and has not flowed into the rear seat heater core 88 .

In the refrigeration cycle device 10 configured in this manner, the air is cooled and blown out to the space in which the driver's seat is provided and the space in which the rear seats are provided, thereby cooling the vehicle interior, but the battery 60 is not cooled. It can also be operated in all-seat cooling mode. Furthermore, the refrigeration cycle device 10 cools the passenger compartment by cooling the blown air and blowing it out to the space where the driver's seat is installed and the space where the rear seats are installed, and cools the battery 60 in an all-seat cooling cooling mode. can drive. The operation of the all-seat cooling/cooling mode will be described below as an example of an operation mode that can be executed by the refrigeration cycle apparatus 10 of the present embodiment.

In the front seat cooling/cooling mode, the control device 70 switches the refrigeration cycle device 10 to the refrigerant circuit in the all-seat cooling/cooling mode. Specifically, the control device 70 causes the third expansion valve 17c to be throttled in addition to operating each component in the cooling cooling mode described above. Based on the detection signals transmitted from the fourth refrigerant temperature sensor 19g and the fourth refrigerant pressure sensor 19h, the control device 70 adjusts the degree of superheat of the outlet-side refrigerant of the rear seat evaporator 14b to a predetermined target degree of superheat. Next, the degree of opening of the third expansion valve 17c is determined.

Therefore, in the refrigeration cycle device 10 in the all-seats cooling/cooling mode, the refrigerant flows in the order of the compressor 12→water-refrigerant heat exchanger 13→refrigerant branch portion 18. FIG. One of the refrigerants branched at the refrigerant branching portion 18 flows in the order of the first expansion valve 17a→the front seat evaporator 14a→the front seat air conditioning inflow pipe 11d→the connection device 200, and the third expansion valve 17c→the rear seat evaporation. It flows in the order of the vessel 14b→the rear seat inflow pipe 11e→the connection device 200.

Refrigerant flowing into the connection device 200 from the front seat air conditioning inflow pipe 11d and the rear seat inflow pipe 11e joins inside the connection device 200 and flows to the compressor 12 through the compressor outflow pipe 11c.

The other refrigerant branched at the refrigerant branching portion 18 flows through the second expansion valve 17b→chiller 16→cooling portion inflow pipe 11b→connecting device 200→compressor outflow pipe 11c→compressor 12 in this order.

Also, in the high temperature side heat medium circuit 30 in the all-seats cooling/cooling mode, the high temperature side heat medium flows in the same manner as in the cooling/cooling mode. Then, in the low-temperature side heat medium circuit 40 in the all-seats cooling/cooling mode, the low-temperature side heat medium flows in the same manner as in the cooling/cooling mode.

In this way, in the all-seat cooling/cooling mode, the refrigerant that has flowed out of the front seat evaporator 14a flows into the connecting device 200 from the series inlet 221 via the front seat air conditioning inlet pipe 11d. Also, the refrigerant flowing out of the rear seat evaporator 14b flows into the connecting device 200 from the second inclined inlet 241 through the rear seat inlet pipe 11e. Further, in the connection device 200, the refrigerant that has flowed out of the chiller 16 flows in from the inclined inlet 231 through the cooling section inflow pipe 11b. Then, the connecting device 200 causes the refrigerant that has flowed in from the series inlet 221, the second inclined inlet 241, and the inclined inlet 231 to flow out from the series outlet 253 and guides it to the compressor outlet pipe 11c.

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

Therefore, in the vehicle air conditioner 1 in the all-seats cooling/cooling mode, the space in which the driver's seat is installed can be cooled by blowing out the blown air cooled by the front seat evaporator 14a to the space in which the driver's seat is installed. can. Further, in the vehicle air conditioner 1 in the all-seats cooling/cooling mode, the air cooled by the rear seat evaporator 14b is blown out to the space in which the rear seats are provided, thereby cooling the space in which the rear seats are provided. can.

Furthermore, the battery 60 can be cooled by circulating the low temperature side heat medium cooled by the chiller 16 . 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 to operate the inverter 61, the motor generator 62, and the transaxle device 63. Allow to cool.

Next, details of the connection device 200 of the present embodiment will be described with reference to FIGS. 16 and 17. FIG. As shown in FIGS. 16 and 17, compared to the second embodiment, the inside of the housing 210 does not penetrate from the surface of the left surface portion 214 to the lower surface portion 212 as the coolant passage. A second inclined upstream channel section 240 is added which extends at an angle.

Second inclined upstream flow path portion 240 extends from a portion of the surface of left surface portion 214 below the center in vertical direction DR1 toward a portion on the right side of the center in horizontal direction DR3 of lower surface portion 212 . In addition, the second inclined upstream flow path portion 240 is provided at the end opposite to the side positioned on the surface of the left surface portion 214 , in the middle of the refrigerant passage different from the both ends of the serial downstream flow path portion 250 . parts are connected.

That is, in the present embodiment, the second inclined upstream channel portion 240 is not directly connected to the series upstream channel portion 220 and the inclined upstream channel portion 230 . Specifically, the portion of the serial downstream flow path portion 250 to which the second inclined upstream flow portion 240 is connected has a higher coolant flow rate than the portion to which the serial upstream flow portion 220 and the inclined upstream flow portion 230 are connected to the serial downstream flow portion 250 . Downstream side. Therefore, the refrigerant flowing through the second inclined upstream flow path portion 240 does not directly join the refrigerant flowing through the serial upstream flow path portion 220 and the inclined upstream flow path portion 230 .

The second inclined upstream flow path portion 240 forms a refrigerant passage for guiding the refrigerant flowing out of the rear seat inflow pipe 11 e into the housing 210 . The second inclined upstream channel portion 240 linearly extends in a direction different from the direction in which the serial upstream channel portion 220, the inclined upstream channel portion 230, and the serial downstream channel portion 250 extend. The second inclined upstream channel portion 240 has a second inclined inlet 241 communicating with the rear seat inflow pipe 11e on the upstream side of the refrigerant flow, and a second inclined confluence port communicating with the serial downstream channel portion 250 on the downstream side of the refrigerant flow. 242. The direction in which the second inclined upstream channel portion 240 extends will be described later.

The second inclined upstream channel portion 240 is formed such that the seventh inner diameter φ7, which is the inner diameter of the second inclined upstream channel portion 240, is slightly larger than the outer diameter of the rear seat inflow pipe 11e. The second inclined upstream channel portion 240 is formed so that the rear seat inflow pipe 11e can be inserted from the second inclined inlet port 241 into the second inclined upstream channel portion 240 . Specifically, the inner diameter of the second inclined upstream channel portion 240 is formed slightly larger than the outer diameter of 15.88 mm of the rear seat inflow pipe 11e.

The second inclined upstream flow path portion 240 is formed such that the seventh inner diameter φ7 is uniform from the refrigerant flow upstream side to the refrigerant flow downstream side. The seventh inner diameter φ7 is the diameter of the cross-sectional shape in the direction perpendicular to the direction in which the second inclined upstream flow path portion 240 extends. In this embodiment, the second inclined upstream flow path portion 240 is formed such that the seventh inner diameter φ7 is smaller than the fourth inner diameter φ4 and the sixth inner diameter φ6 and equal to the fifth inner diameter φ5.

In addition, the series downstream flow path portion 250 of the present embodiment includes a downstream merging portion 252 that joins the refrigerant flowing through the second inclined upstream flow path portion 240 to the series downstream flow path portion 250 on the refrigerant flow downstream side of the plurality of merging portions 251 . have.

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

In the present embodiment, in the serial downstream channel portion 250, the position where the serial upstream channel portion 220 and the inclined upstream channel portion 230 join and the position where the second inclined upstream channel portion 240 joins are provided at different positions. there is Then, the refrigerant flowing through the series upstream channel portion 220 and the inclined upstream channel portion 230 flows into the multiple confluence portion 251 . In addition, the refrigerant that has flowed from the serial upstream flow path portion 220 and the inclined upstream flow path portion 230 into the serial downstream flow path portion 250 and the refrigerant that flows through the second inclined upstream flow path portion 240 flow into the downstream joining portion 252 . In the present embodiment, the multiple confluence section 251 and the downstream confluence section 252 function as confluence sections.

Further, the serial downstream flow path portion 250 is formed such that the sixth inner diameter φ6 is larger than the seventh inner diameter φ7. That is, the serial downstream flow path portion 250 is formed such that the inner diameter on the downstream side of the refrigerant flow from the downstream confluence portion 252 is larger than the inner diameter of the second inclined upstream flow path portion 240 .

In other words, in the series downstream flow path portion 250 , the flow path cross-sectional area of the cross section orthogonal to the refrigerant flow direction is in the flow direction of the refrigerant in the second inclined upstream flow path portion 240 on the downstream side of the flow of the refrigerant from the downstream confluence portion 252 . It is formed larger than the channel cross-sectional area of the orthogonal cross section. The serial outflow port 253 is positioned below the second inclined inflow port 241 in the vertical direction.

Subsequently, the details of the direction in which the second inclined upstream channel portion 240 extends will be described using a predetermined confluence reference direction DRC. The predetermined confluence reference direction DRC is an upward direction along the vertical direction DR1, and is an upward direction along the vertical direction DR1 with the multiple confluence portion 251 and the downstream confluence portion 252 as a reference.

The second inclined upstream flow path portion 240 extends at a fourth angle θ4 larger than 0° and smaller than 90° with respect to the predetermined confluence reference direction DRC with the downstream confluence portion 252 as a reference. Here, the angle extending from the downstream merging portion 252 deviated from the predetermined merging reference direction DRC means that the upper side of the vertical direction DR1 is 0° and the counterclockwise direction is positive in the cross-sectional view shown in FIG. This is the angle to be oriented. The fourth angle θ4 is an angle formed by the predetermined confluence reference direction DRC and the direction in which the second inclined upstream flow path portion 240 extends, with the downstream confluence portion 252 being the center.

In this embodiment, the second inclined upstream flow path portion 240 extends so that the fourth angle θ4 is the same angle as the third angle θ3, that is, 45°. Thus, the direction in which the second inclined upstream flow path portion 240 of the present embodiment extends includes the left-right direction DR3 and the up-down direction DR1, but does not include the front-rear direction DR2. The fourth angle θ4 may be larger than or smaller than the third angle θ3 as long as it is in the range of greater than 0° and less than 90°.

Next, the refrigerant flow and pressure loss when the refrigerant flows through the connection device 200 of the present embodiment when the refrigeration cycle device 10 is operated in the all-seats cooling mode will be described with reference to FIG. 18 .

In the all-seat cooling/cooling mode, the refrigerant flows into the connecting device 200 from the series inlet 221 through the front seat air conditioning inlet pipe 11d. In addition, the coolant flows into the connection device 200 from the inclined inlet 231 through the cooling section inlet pipe 11b. Further, the refrigerant flows into the connection device 200 from the second inclined inlet 241 through the rear seat inlet pipe 11e.

18, the refrigerant that has flowed in from the serial inlet 221 flows downward in the vertical direction DR1 along the direction in which the serial upstream channel portion 220 extends, and flows through the serial confluence port 222. It flows into the serial downstream flow section 250 . Refrigerant that has flowed in from the inclined inlet 231 flows along the direction in which the inclined upstream flow path portion 230 extends, and flows into the serial downstream flow path portion 250 from the inclined confluence port 232, as indicated by refrigerant flow F8 in FIG.

Then, the refrigerants flowing into the serial downstream flow path portion 250 from the series confluence port 222 and the inclined confluence port 232 merge and collide with each other, and then move toward the downstream confluence portion 252 in the direction in which the serial downstream flow path portion 250 extends. along the vertical direction DR1 toward the lower side.

When the refrigerant that has flowed into the series downstream flow path portion 250 from the series junction port 222 flows into the series downstream flow path portion 250, the flow direction of the refrigerant is substantially unchanged and flows toward the downstream side of the flow of the refrigerant. On the other hand, the refrigerant that has flowed into the series downstream flow path portion 250 from the inclined confluence port 232 changes its flow direction by 45°, which is the third angle θ3, when flowing into the series downstream flow path portion 250. flows toward the downstream side.

The flow velocity vector of the refrigerant flowing from the multiple merging portion 251 toward the downstream merging portion 252 has a downward flow velocity vector component in the vertical direction DR1 and does not have flow velocity vector components in other directions. That is, in the serial downstream flow path portion 250, the flow velocity vector of the refrigerant flowing upstream of the downstream junction portion 252 and immediately before flowing into the downstream junction portion 252 is the downward flow velocity vector component in the vertical direction DR1. and have no velocity vector components in other directions.

18, the refrigerant that has flowed in from the second inclined inlet 241 flows along the direction in which the second inclined upstream channel portion 240 extends, and flows from the second inclined confluence port 242 to the serial downstream channel. Flow into section 250 .

The flow velocity vector of the refrigerant flowing along the direction in which the second inclined upstream flow path portion 240 extends has a downward flow velocity vector component in the vertical direction DR1 and a rightward flow velocity vector component in the lateral direction DR3, and a flow velocity in the longitudinal direction DR2. has no vector components. That is, the flow velocity vector of the refrigerant flowing through the second inclined upstream flow path portion 240 and immediately before flowing into the downstream confluence portion 252 has a downward flow velocity vector component in the vertical direction DR1 and a rightward flow velocity vector component in the horizontal direction DR3. and does not have a flow velocity vector in the longitudinal direction DR2.

The refrigerant flowing from the second inclined confluence port 242 into the serial downstream flow passage portion 250 joins and collides with the refrigerant flowing into the serial downstream flow portion 250 from the serial confluence ports 222 and 232 . The refrigerant that has flowed into the series downstream flow path portion 250 from the second inclined confluence port 242 changes its flow direction by 45°, which is the fourth angle θ4, when flowing into the series downstream flow path portion 250. flows downstream.

After that, the refrigerant that has flowed into the serial downstream flow path portion 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 confluence portion 252, and the serial flow It flows out from the outlet 253 to the compressor outflow pipe 11c.

As described above, in the connection device 200 of the present 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. Other configurations and operations of the connection device 200 are the same as those of the second embodiment. According to this, an effect similar to that of the first embodiment can be obtained.

In addition, the refrigerant flowing from the second inclined confluence port 242 into the serial downstream flow passage portion 250 joins and collides with the refrigerant flowing into the serial downstream flow portion 250 from the serial confluence port 222 and the slanted confluence port 232. The direction is changed by 45°. The refrigerant that has flowed into the series downstream flow path portion 250 from the second inclined confluence port 242 flows downward in the vertical direction DR1 together with the refrigerant that has flowed in from the series confluence port 222 and the inclined confluence port 232 .

Therefore, in the connection device 200 of the present embodiment, compared to the case where the second inclined upstream flow path portion 240 extends with a deviation of 90° from the predetermined confluence reference direction DRC, the amount of change in the refrigerant flow direction is reduced. can be made smaller. Therefore, it is possible to suppress the pressure loss when the flow direction of the refrigerant changes.

In addition, in the connection device 200 of the present embodiment, the refrigerant flowing from the plurality of merging portions 251 toward the downstream merging portion 252 opposes the refrigerant flowing from the second inclined upstream flow path portion 240 to the series downstream flow path portion 250. Does not include directional velocity vectors. Therefore, pressure loss caused by collision when the refrigerant joins from the second inclined upstream flow path portion 240 to the series downstream flow path portion 250 can be suppressed as compared to the case where such a configuration is not adopted.

(1) In the above embodiment, the serial downstream flow path portion 250 is formed such that the inner diameter on the downstream side of the downstream junction portion 252 in the refrigerant flow is larger than the inner diameter of the second inclined upstream flow path portion 240 .

Therefore, in the serial downstream flow path portion 250 , the flow velocity of the refrigerant flowing downstream of the downstream junction portion 252 is such that the inner diameter of the downstream side of the downstream junction portion 252 is the inner diameter of the second inclined upstream flow path portion 240 . It is slower than when it is formed below the size of . Therefore, compared to the case where the inner diameter of the serial downstream flow path portion 250 is equal to or less than the inner diameter of the second inclined upstream flow path portion 240, the pressure loss generated when the refrigerant flows through the serial downstream flow path portion 250 is suppressed. can do.

(2) In the above embodiment, the connection device 200 has the front air conditioning inflow pipe 11d connected to the serial upstream passage portion 220 .

Here, in the vehicle air conditioner 1 mounted on the electric vehicle, air conditioning in the vehicle interior is relatively emphasized rather than cooling the battery 60 . In the vehicle air conditioner 1, more emphasis is placed on air-conditioning the space in which the driver's seat is provided than in the space in which the rear seats are provided in the vehicle interior. Furthermore, in the vehicle air conditioner 1, cooling of the battery 60 is considered more important than air conditioning of the space in which the rear seats are provided.

Therefore, in the refrigeration cycle device 10 that operates in the all-seat cooling/cooling mode, more refrigerant flows through the front seat air conditioning inflow pipe 11d than into the cooling portion inflow pipe 11b, and more into the cooling portion inflow pipe 11b than the rear seat inflow pipe 11e. of refrigerant must flow. In this case, in the connection device 200 , the largest amount of refrigerant flows into the serial upstream channel portion 220 among the three upstream channel portions 220 , 230 and 240 . In the refrigeration cycle apparatus 10 as a whole, the pressure loss generated when joining the serial downstream flow section 250 has a greater effect on the serial upstream flow section 220, the inclined upstream flow section 230, and the second inclined upstream flow section 240 in that order. .

In the above embodiment, of the three upstream flow paths 220, 230, and 240, the front air conditioning inflow pipe 11d is connected to the series upstream flow path 220 in which the refrigerant flow direction does not substantially change. Therefore, when the refrigerant merges from each of the three upstream flow passages 220, 230, and 240 into the series downstream flow passage 250, it is easy to suppress the pressure loss when the flow direction of the refrigerant changes in the refrigeration cycle device 10 as a whole. . Therefore, when the most refrigerant flows through the front seat air conditioning inflow pipe 11d, the pressure loss of the entire refrigeration cycle device 10 can be suppressed as compared with the case where the structure is not configured in this manner.

(3) In the above-described embodiment, in the serial downstream flow path section 250, the multiple confluence section 251 and the downstream confluence section 252 are provided at different positions. Therefore, when the three upstream flow path sections 220, 230, and 240 merge at the serial downstream flow path section 250, the position where the serial upstream flow path section 220 and the inclined upstream flow path section 230 merge and the second inclined upstream flow path section 240 merge. position can be shifted.

Therefore, when the coolant flows into the serial downstream channel portion 250 from the upstream flow channel portions 220 and 230 connected to the plurality of confluence portions 251, it is possible to avoid colliding with the coolant joining from the second inclined upstream flow channel portion 240. . As a result, pressure loss due to collision when the refrigerant joins in the serial downstream flow path portion 250 can be suppressed as compared to a case without such a configuration.

(4) In the above-described embodiment, the connecting device 200 has the front air conditioning inflow pipe 11d connected to the serial upstream channel portion 220, and the cooling portion inflow pipe 11b connected to the inclined upstream channel portion 230. As shown in FIG. In addition, the connection device 200 has a second inclined upstream flow path portion 240 connected to the rear seat inflow pipe 11e. The plurality of junctions 251 is provided at a position upstream of the downstream junction 252 in the refrigerant flow.

Further, as described above, in the serial downstream flow path portion 250, if there is a refrigerant passage that merges with the refrigerant passage on the way from the upstream side of the refrigerant flow to the downstream side of the serial downstream flow portion 250, the merging refrigerant passage A force is generated that draws the inflowing refrigerant into the serial downstream flow path portion 250 . The force that draws in the serial downstream flow path portion 250 increases as the amount of refrigerant flowing through the serial downstream flow path portion 250 increases.

In the refrigeration cycle device 10 that operates in the all-seats cooling/cooling mode, more refrigerant flows into the inclined upstream passage portion 230 than the second inclined upstream passage portion 240, and more refrigerant flows into the series upstream passage portion 220 than into the inclined upstream passage portion 230. A lot of refrigerant flows into

In the above-described embodiment, the plurality of junctions 251 is provided at a position upstream of the downstream junction 252 in the refrigerant flow. Therefore, the coolant flowing through the second inclined upstream channel portion 240 merges with the serial downstream channel portion 250 through which the coolant flowing from the serial upstream channel portion 220 and the inclined upstream channel portion 230 flows. Therefore, in the series downstream flow path portion 250 , the flow rate of the refrigerant flowing upstream of the downstream junction portion 252 can be increased compared to the case of not having such a configuration. Therefore, the refrigerant flowing through the serial downstream flow path portion 250 can increase the force that draws the refrigerant from the second inclined confluence port 242 to the serial downstream flow passage portion 250, thereby suppressing pressure loss when the flow direction of the refrigerant changes. can be done.
(First Modification of Third Embodiment)
In the above-described third embodiment, an example in which the third angle θ3 and the fourth angle θ4 have the same size has been described, but the present invention is not limited to this. For example, the inclined upstream channel portion 230 may be configured such that the third angle θ3 is smaller than the fourth angle θ4.

According to this, the amount of change in the flow direction of the refrigerant when joining the series downstream flow section 250 from the inclined upstream flow section 230 is smaller than when joining the series downstream flow section 250 from the second inclined upstream flow section 240. Become. For this reason, compared to the pressure loss when the flow direction of the refrigerant changes when joining the serial downstream flow section 250 from the second inclined upstream flow section 240, the flow direction of the refrigerant flowing from the inclined upstream flow section 230 to the serial downstream flow section 250 is reduced. It is possible to suppress the pressure loss when the flow direction of the refrigerant changes.

Further, when more refrigerant flows through the cooling portion inflow pipe 11b than in the rear seat inflow pipe 11e, the pressure loss of the entire refrigeration cycle device 10 can be suppressed as compared with the case where this configuration is not provided.
(Second modification of the third embodiment)
In the above-described third embodiment, an example has been described in which the inner diameter of the serial downstream channel portion 250 and the inner diameter of the serial upstream channel portion 220 are formed to have the same size, but the present invention is not limited to this. For example, when the outer diameter of the front seat air conditioning inflow pipe 11d is the same as the outer diameter of the rear seat inflow pipe 11e and the outer diameter of the cooling unit inflow pipe 11b, the inner diameter of the serial upstream channel portion 220 is the same as that of the serial downstream channel portion 250. It may be configured to be smaller than the inner diameter. Specifically, the inner diameter of the serial upstream channel portion 220 may be the same as the inner diameters of the inclined upstream channel portion 230 and the second inclined upstream channel portion 240 .
(Third Modification of Third Embodiment)
In the above-described third embodiment, the serial downstream flow path portion 250 has an equal inner diameter from the most upstream portion of the refrigerant flow to the serial outlet 253 via the multiple confluence portion 251 and the downstream confluence portion 252. has been described, but is not limited to this. For example, as shown in FIG. 19, the serial downstream channel portion 250 has an inner diameter that gradually increases from the most upstream portion of the refrigerant flow to the serial outlet 253 via the multiple merging portion 251 and the downstream merging portion 252. may be configured to Specifically, in the serial downstream flow path portion 250, the inner diameter of the portion provided with the multiple merging portions 251 is larger than that of the most upstream portion of the refrigerant flow, and the inner diameter of the portion provided with the downstream merging portion 252 is the multiple merging portions. The inner diameter may be formed larger than the portion where 251 is provided.

As a result, the flow velocity of the refrigerant in the serial downstream flow path portion 250 becomes slower as the inner diameter increases. Therefore, in the series downstream flow path section 250, the pressure loss that occurs when the refrigerant flows through the series downstream flow path section 250 can be suppressed as compared to the case where the series downstream flow path section 250 is not configured in this way.
(Fourth modification of the third embodiment)
In the above-described third embodiment, an example has been described in which the outer diameters of the front seat air conditioning inflow pipe 11d, the cooling section inflow pipe 11b, and the rear seat inflow pipe 11e are formed to be equal from the inlet side to the outlet side. is not limited to For example, as shown in FIG. 20, the front air conditioning inflow pipe 11d has an outer diameter that increases in the middle of the flow path from the refrigerant flow upstream side toward the refrigerant flow downstream side, and the outlet side is inserted into the in-line upstream flow path portion 220. It may be formed so as to be In addition, the cooling portion inflow pipe 11b has an outer diameter that increases in the middle of the flow path from the upstream side of the refrigerant flow toward the downstream side of the refrigerant flow, and the outlet side is formed so as to be inserted into the inclined upstream flow path portion 230. good too. In addition, the rear seat inflow pipe 11e has an outer diameter that increases in the middle of the flow path from the upstream side of the refrigerant flow toward the downstream side of the refrigerant flow, and is formed such that the outlet side is inserted into the second inclined upstream flow path portion 240. may be

As a result, in the front air conditioning inflow pipe 11d, the flow velocity of the refrigerant flowing downstream of the portion with the larger outer diameter is lower than the flow velocity of the refrigerant flowing upstream of the portion with the larger outer diameter. In addition, in the cooling section inflow pipe 11b, the flow velocity of the refrigerant flowing downstream of the portion with the larger outer diameter is slower than the flow velocity of the refrigerant flowing upstream of the portion with the larger outer diameter. In addition, in the rear seat inflow pipe 11e, the flow velocity of the refrigerant flowing downstream of the portion having the larger outer diameter is slower than the flow velocity of the refrigerant flowing upstream of the portion having the larger outer diameter.

Therefore, the pressure loss generated when the refrigerant flows through each of the front seat air conditioning inflow pipe 11d, the cooling part inflow pipe 11b, and the rear seat inflow pipe 11e can be suppressed as compared with the case where the structure is not configured in this way. .

(Fourth embodiment)
Next, a fourth embodiment will be described with reference to FIG. A connection device 300 of this embodiment differs from that of the second embodiment in the shape of a housing 310 . In this embodiment, portions different from the second embodiment will be mainly described, and descriptions of portions similar to the second embodiment may be omitted.

The housing 310 of the present embodiment is formed by connecting a plurality of cylindrical refrigerant passage forming portions. Specifically, the housing 310 includes a first cylindrical portion 311 in which the first cylinder upstream flow passage portion 320 and the cylinder downstream flow passage portion 350 are formed, and a second cylindrical portion in which the second cylinder upstream flow passage portion 330 is formed. 312.

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 is formed with a refrigerant passage through which a refrigerant flows. Also, 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 that has flowed in from one side in the vertical direction DR1 can flow through the internal refrigerant passage and can flow out from the other side in the vertical direction DR1. A second cylindrical portion 312 is connected to substantially the center of the outer peripheral portion of the first cylindrical portion 311 in the vertical direction DR1.

The second cylindrical portion 312 has a hollow cylindrical shape and extends obliquely upward in the vertical direction DR1 and rightward in the horizontal direction DR3 from a portion connected to the first cylindrical portion 311 as a starting point. The second cylindrical portion 312 is formed with a coolant passage through which coolant flows. Also, 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 connected to the first cylindrical portion 311 .

In this embodiment, the connection device 300 has a first cylinder upstream flow path portion 320 and a cylinder downstream flow channel portion 350 inside the first cylindrical portion 311 . A portion of the refrigerant passage formed inside the first cylindrical portion 311 that extends from the upper end in the vertical direction DR<b>1 to the portion communicating with the refrigerant passage of the second cylindrical portion 312 is the first cylinder upstream passage portion 320 . The first cylinder upstream flow path portion 320 corresponds to the serial upstream flow path portion 220 of the second embodiment. In this embodiment, the first cylinder upstream channel portion 320 functions as a series upstream channel portion.

Further, in the refrigerant passage formed inside the first cylindrical portion 311 , a portion from a portion communicating with the refrigerant passage of the second cylindrical portion 312 to the lower end portion in the vertical direction DR1 is a cylinder downstream passage portion 350 . The cylinder downstream flow path portion 350 corresponds to the serial downstream flow path portion 250 of the second embodiment. In the present embodiment, the cylinder downstream channel portion 350 functions as a downstream channel portion.

That is, of the refrigerant passage formed inside the first cylindrical portion 311, a portion above the approximate center in the vertical direction DR1 is configured as the first cylinder upper passage portion 320 that allows the refrigerant to flow into the connection device 300. It is In addition, of the refrigerant passage formed inside the first cylindrical portion 311, a portion below the approximate center in the vertical direction DR1 is configured as a cylinder downstream passage portion 350 through which the refrigerant flows out from the connection device 300. .

In this embodiment, the connection device 300 has the second cylinder upper flow path portion 330 inside the second cylindrical portion 312 . The second cylinder upstream passage portion 330 corresponds to the inclined upstream passage portion 230 of the second embodiment. That is, the refrigerant passage formed inside the second cylindrical portion 312 is configured as the second cylinder upper flow passage portion 330 that allows the refrigerant to flow into the connection device 300 . In this embodiment, the second cylinder upstream channel portion 330 functions as an inclined upstream channel portion.

The first cylinder upstream flow path portion 320 extends linearly along the direction in which the first cylindrical portion 311 extends, that is, along the vertical direction DR1. In addition, the first cylinder upstream channel portion 320 has a first cylinder inlet 321 to which the air conditioning inflow pipe 11a is connected at the upper end in the vertical direction DR1, and the lower end in the vertical direction DR1, The upper end in the up-down direction DR1 of the downstream tube portion 350 communicates with each other.

The second cylinder upstream flow path portion 330 extends obliquely in the direction in which the second cylindrical portion 312 extends, that is, upward in the up-down direction DR1 and rightward in the left-right direction DR3. In addition, the upper end of the cylinder downstream flow path portion 350 in the up-down direction DR1 is connected to the end of the first cylindrical portion 311 on the side communicating with the refrigerant passage among both ends of the second cylinder upstream flow channel portion 330 . It is The second cylinder upper flow passage portion 330 is connected to the cooling portion inflow pipe 11b at one of both end portions of the first cylindrical portion 311 opposite to the end communicating with the refrigerant passage. It has a two-cylinder inlet 331 .

The downstream channel portion 350 extends linearly along the direction in which the first cylindrical portion 311 extends, that is, along the vertical direction DR1. Further, the cylinder downstream flow path portion 350 is connected to the first cylinder upstream flow path portion 320 and the second cylinder upstream flow path portion 330 at the upper end portion in the vertical direction DR1, and is connected to the lower end portion in the vertical direction DR1. , and a cylindrical outlet 353 to which the compressor outlet pipe 11c is connected.

The downstream cylinder flow path portion 350 has a cylindrical confluence portion 351 that joins the refrigerant flowing through the first upstream cylinder flow path portion 320 and the second upstream cylinder flow path portion 330 into the downstream cylinder flow path portion 350 on the upstream side of the refrigerant flow. In this embodiment, the cylindrical junction 351 functions as a junction.

In this manner, the ends of the first cylinder upstream flow path portion 320 and the second cylinder upstream flow path portion 330 are connected to each other at the ends to which the respective cylinder downstream flow path portions 350 are connected. That is, the most downstream refrigerant flow portion of the first cylinder upstream passage portion 320 and the most downstream refrigerant flow portion of the second cylinder upstream passage portion 330 are directly connected to the most upstream refrigerant flow portion of the cylinder downstream passage portion 350 .

The first cylinder upstream channel portion 320 extends along a predetermined confluence reference direction DRC. Therefore, the angle formed by the predetermined confluence reference direction DRC and the direction in which the first cylinder upper flow path portion 320 extends is 0° with the cylindrical confluence portion 351 as the center. On the other hand, the second cylinder upper flow passage portion 330 extends with a deviation of 45° from the predetermined confluence reference direction DRC.

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. Other configurations and operations of the connection device 300 are the same as those of the second embodiment. According to this, an effect similar to that of the second embodiment can be obtained.

(Other embodiments)
Although representative embodiments of the present disclosure have been described above, the present disclosure is not limited to the above-described embodiments, and can be modified in various ways, for example, as follows.

In the above-described embodiments, an example in which the connection devices 100, 200, and 300 merge the refrigerants flowing from a plurality of refrigerant pipes and guide them into one refrigerant pipe has been described, but the present invention is not limited to this. For example, as shown in FIG. 22, the connection device 500 may have a configuration in which the refrigerant flowing from one refrigerant pipe is branched inside the connection device 500 to flow out to a plurality of refrigerant pipes.

For example, in the refrigeration cycle device 10, when the connection device 500 is arranged in place of the refrigerant branching unit 18, the connection device 500 branches the refrigerant flowing from the water-refrigerant heat exchanger 13 to the first expansion valve 17a and It may be configured to lead to the second expansion valve 17b.

In this case, as shown in FIG. 22, inside the connection device 500, there is an upstream side stream connected to a refrigerant pipe 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. A channel 510 is provided. Further, inside the connection device 500, there are provided a downstream flow passage portion 520 connected to a refrigerant pipe that guides the refrigerant that has flowed into the connection device 500 to the inlet side of the first expansion valve 17a, and a second expansion valve 17b. A downstream channel portion 530 connected to a refrigerant pipe leading to the inlet side is provided.

Here, a branching portion 540 is a portion where the refrigerant that has flowed into the upstream channel portion 510 is branched, and the upstream channel portion 510 extends from the branching portion 540 toward the upstream side of the upstream channel portion 510 in the flow of the coolant. is the upstream direction. The direction opposite to the upstream direction is defined as a predetermined branch reference direction DRC2. In this case, the downstream channel portion 520 and the downstream channel portion 530 extend with a deviation of an angle larger than 0° and smaller than 90° with respect to the predetermined branch reference direction DRC2.

According to this, compared to the case where the downstream flow path portion 520 and the downstream flow path portion 530 extend with a deviation of 90° from the predetermined branch reference direction DRC2, the amount of change in the flow direction of the refrigerant is reduced. Therefore, it is possible to suppress the pressure loss when the flow direction of the refrigerant changes.

In the above-described embodiments, examples were described in which two or three upstream passage portions were formed inside the connection devices 100, 200, and 300, but the present invention is not limited to this. For example, the connection devices 100, 200, and 300 may have a configuration in which four or more upstream flow paths are formed.

In the above-described embodiment, the steep upstream channel portion 120 and the low upstream channel portion 130 formed in the connection device 100 extend at an angle larger than 0° and smaller than 90° with respect to the predetermined confluence reference direction DRC. Although an example has been described, it is not limited to this. For example, of the steep upstream channel portion 120 and the low upstream channel portion 130 formed in the connection device 100, one upstream channel part A configuration in which they are shifted and extended may also be used. In this case, the other upstream flow path portion extends at an angle larger than 0° and smaller than 90° with respect to the predetermined confluence reference direction DRC.

In the above-described embodiment, an example in which the inner diameter of the downstream channel portion 140 is larger than the inner diameter of the steep upstream channel portion 120 and the inner diameter of the low upstream channel portion 130 has been described, but the present invention is not limited to this. Also, an example has been described in which the inner diameter of the serial downstream channel portion 250 is larger than the inner diameter of the inclined upstream channel portion 230 and the inner diameter of the second inclined upstream channel portion 240, but the present invention is not limited to this.

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

In the above-described embodiment, the air conditioning inflow pipe 11a is connected to the rapid upstream channel portion 120, the cooling portion inflow pipe 11b is connected to the low upstream channel portion 130, and the compressor outflow pipe 11c is connected to the downstream channel portion 140. Although an example has been described, it is not limited to this. Further, in the above-described embodiment, the front seat air conditioning inflow pipe 11d is connected to the serial upstream channel portion 220, the cooling portion inflow pipe 11b is connected to the inclined upstream channel portion 230, and the rear seat inflow pipe is connected to the second inclined upstream channel portion 240. Although an example in which the pipe 11e is connected and the serial downstream flow path portion 250 is connected to the compressor outflow pipe 11c has been described, the present invention is not limited to this. Refrigerant pipes connected to each of the flow paths 120, 130, 140, 220, 230, 240, and 250 can be changed as appropriate.

In the above-described embodiment, an example has been described in which the ratio of the inner diameter of the downstream channel portion 140 to the inner diameter of the steep upstream channel portion 120 and the inner diameter of the low upstream channel portion 130 is 1.20, but the present invention is not limited to this. Also, an example has been described in which the ratio of the inner diameter of the serial downstream flow section 250 to the inner diameter of the inclined upstream flow section 230 and the inner diameter of the second inclined upstream flow section 240 is 1.20, but the present invention is not limited to this.

The ratio of the inner diameter of the downstream channel portion 140 to the inner diameter of the steep upstream channel portion 120 and the inner diameter of the low upstream channel portion 130 can be appropriately changed according to the outer diameters of the refrigerant pipes connected thereto. In addition, the ratio of the inner diameter of the serial downstream flow section 250 to the inner diameter of the inclined upstream flow section 230 and the inner diameter of the second inclined upstream flow section 240 can be appropriately changed according to the outer diameter of the refrigerant pipes connected thereto. .

In the above-described embodiment, the example in which the refrigerant outlet 143 is positioned below the rapid inlet 121 and the low inlet 131 in the vertical direction has been described, but the present invention is not limited to this. In addition, in the above-described embodiment, an example in which the serial outlet 253 is positioned below the serial inlet 221, the inclined inlet 231, and the second inclined inlet 241 in the vertical direction has been described, but the present invention is limited to this. not.

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 . Further, the connection device 200 may be configured such that the serial outlet 253 is positioned above the serial inlet 221 , the inclined inlet 231 , and the second inclined inlet 241 in the vertical direction.

In the above-described embodiments, the inner diameters of the rapid upstream flow path portion 120, the low upstream flow path portion 130, the serial upstream flow path portion 220, the inclined upstream flow path portion 230, and the second inclined upstream flow path portion 240 are the same as those of the refrigerant pipes to which they are connected. Although an example in which the size is formed corresponding to the most downstream portion of the refrigerant flow has been described, the present invention is not limited to this. Further, in the above-described embodiment, the inner diameters of the downstream channel portion 140 and the serial downstream channel portion 250 are respectively formed to have a size corresponding to the most upstream portion of the refrigerant flow of the refrigerant pipe to which they are connected. Illustrated, but not limited to.

For example, the inner diameter of each of the rapid upstream flow path portion 120, the low upstream flow path portion 130, the serial upstream flow path portion 220, the inclined upstream flow path portion 230, and the second inclined upstream flow path portion 240 is the most downstream of the refrigerant flow of the refrigerant pipe to which they are connected. It may be formed in a size that does not correspond to the part. Further, the inner diameters of the downstream channel portion 140 and the serial downstream channel portion 250 may be formed with sizes that do not correspond to the most upstream portion of the refrigerant flow of the refrigerant pipe to which they are connected.

In this case, by using a refrigerant pipe converting portion having an inlet side outer diameter and an outlet side outer diameter different in size, the refrigerant pipes to which the respective upstream flow passage portions and the respective downstream flow passage portions are connected are connected. can be connected to

In the above-described embodiment, an example is described in which the respective refrigerant passages formed inside the connection devices 100, 200, and 300 are formed in a straight line from the upstream side to the downstream side of the refrigerant flow, but the present invention is limited to this. not. For example, each coolant passage formed inside the connection devices 100, 200, and 300 may be formed including a curved portion.

In the above-described embodiments, it goes without saying that the elements that make up the embodiments are not necessarily essential unless explicitly stated as essential or clearly considered essential in principle.

In the above-described embodiments, when numerical values such as the number, numerical value, amount, range, etc. of the constituent elements of the embodiment are mentioned, when it is explicitly stated that they are essential, and in principle they are clearly limited to a specific number It is not limited to that particular number, unless otherwise specified.

In the above-described embodiments, when referring to the shape, positional relationship, etc. of components, etc., the shape, positional relationship, etc., unless otherwise specified or limited in principle to a specific shape, positional relationship, etc. etc. is not limited.

REFERENCE SIGNS LIST 100 connection device 110 housing 120, 130 upstream channel portion 140 downstream channel portion 141, 142 confluence portion

Claims (15)

In a refrigeration cycle device (10) in which a refrigerant circulates, at least one inflow pipe (11a, 11b, 11d, 11e) and at least one outflow pipe (11c) are connected, and the refrigerant flowing from the inflow pipe is connected to the inflow pipe. A connection device that leads to the outflow pipe provided on the downstream side of the refrigerant flow from the pipe,
a housing (110, 210, 310);
upstream flow path portions (120, 130, 220, 230, 240, 320, 330, 510) that are connected one-to-one to the inflow pipe and allow the refrigerant to flow into the interior of the housing;
The downstream flow path section ( 140, 250, 350, 520, 530) and
a merging portion (141, 142, 251, 252, 351) for joining the refrigerant flowing from the plurality of upstream flow passage portions to the downstream flow passage portion; Either one of the branching parts (540) that branches to the side channel part,
When the confluence portion is provided, when the direction in which the downstream flow path portion extends from the confluence portion toward the downstream side of the refrigerant flow of the downstream flow path portion is defined as the downstream direction, the plurality of upstream flow path portions at least one extends at an angle greater than 0° and less than 90° with respect to the downstream direction;
When the branch portion is provided, when the direction in which the upstream channel portion extends from the branch portion toward the upstream side of the refrigerant flow of the upstream channel portion is defined as the upstream direction, the plurality of downstream channel portions At least one connecting device extending at an angle greater than 0° and less than 90° with respect to said upstream direction. Having a plurality of upstream flow path sections connected to a plurality of inflow pipes,
Having one said downstream channel portion connected to one said outflow pipe,
2. The connection device according to claim 1, wherein the plurality of upstream channel portions extend at an angle larger than 0[deg.] and smaller than 90[deg.] with respect to the downstream direction. The plurality of upstream channel portions include a first inclined upstream channel portion (120) extending along a direction shifted by an angle larger than 0° and smaller than 90° with respect to the downstream direction; A second inclined upstream channel portion ( 130). The downstream channel portion has an inner diameter on the downstream side of the refrigerant flow from a portion to which the first inclined upstream channel portion is connected, which is larger than the inner diameter of the first inclined upstream channel portion, and the second inclined upstream channel portion. 4. The connection device according to claim 3, wherein the inner diameter of the downstream side of the flow of the coolant from the portion to which the flow path is connected is larger than the inner diameter of the second inclined upstream flow path. The refrigeration cycle device is applied to a vehicle air conditioner, and includes a compressor (12) that compresses and discharges refrigerant drawn in, and a space to be air-conditioned using the discharged refrigerant discharged from the compressor as a heat source. a heating unit (13, 30) for heating the air blown to the air conditioning heat exchanger (13, 30) for evaporating the refrigerant flowing out of the heating unit and cooling the blown air before being heated by the heating unit (13, 30) (14), and a cooling unit (16, 40) that evaporates the refrigerant flowing out of the heating unit and cools an object to be cooled that is different from the blown air,
The plurality of inflow pipes include an air conditioning inflow pipe (11a) through which the refrigerant flowing out from the air conditioning heat exchanger flows, and a cooling unit inflow pipe (11b) through which the refrigerant flowing out from the cooling unit flows,
The outflow pipe is a compressor outflow pipe (11c) that guides refrigerant to the compressor,
The first inclined upstream channel portion is connected to the air conditioning inflow pipe,
The second inclined upstream channel portion is connected to the cooling portion inflow pipe,
The downstream channel portion is connected to the compressor outflow pipe,
5. The connection according to claim 3 or 4, wherein the direction in which the first inclined upstream channel portion extends in the downstream direction is smaller than the direction in which the second inclined upstream channel portion extends in the downstream direction. Device. The plurality of upstream flow passage portions are arranged in a direction different from the direction in which the serial upstream flow passage portions (220, 320) extend along the downstream direction and the direction in which the serial upstream flow passage portions extend. 3. The connecting device according to claim 2, comprising an inclined upstream channel portion (230, 330) extending along a direction offset by an angle greater than 0[deg.] and less than 90[deg.] with respect to the direction. 7. The connection device according to claim 6, wherein the downstream flow passage portion has an inner diameter on the downstream side of the flow of the coolant from a portion to which the inclined upstream flow passage portion is connected, which is larger than the inner diameter of the inclined upstream flow passage portion. The refrigeration cycle device is applied to a vehicle air conditioner, and includes a compressor (12) that compresses and discharges refrigerant drawn in, and a space to be air-conditioned using the discharged refrigerant discharged from the compressor as a heat source. a heating unit (13, 30) for heating the air blown to the air conditioning heat exchanger (13, 30) for evaporating the refrigerant flowing out of the heating unit and cooling the blown air before being heated by the heating unit (13, 30) (14), and a cooling unit (16, 40) that evaporates the refrigerant flowing out of the heating unit and cools an object to be cooled that is different from the blown air,
The plurality of inflow pipes are an air conditioning inflow pipe (11a) through which the refrigerant flowing out from the air conditioning heat exchanger flows, and a cooling unit inflow pipe (11b) through which the refrigerant flowing out from the cooling unit flows,
The outflow pipe is a compressor outflow pipe (11c) that guides refrigerant to the compressor,
The serial upstream channel portion is connected to the air conditioning inflow pipe,
The inclined upstream channel portion is connected to the cooling portion inflow pipe,
The connection device according to claim 6 or 7, wherein the downstream flow path portion is connected to the compressor outflow pipe. The plurality of upstream flow passage portions are arranged in a series upstream flow passage portion (220) extending along the downstream direction and in a direction different from the direction in which the serial upstream flow passage portions extend in the downstream direction. a first inclined upstream channel portion (230) extending along a direction shifted by an angle larger than 0° and smaller than 90° with respect to the direction in which the serial upstream channel portion extends and the first inclined upstream side A second inclined upstream channel portion (240) extending along a direction different from the direction in which the channel portion extends and shifted from the downstream direction by an angle larger than 0° and smaller than 90°. 3. The connection device according to claim 2, comprising: The downstream channel portion has an inner diameter on the downstream side of the flow of the coolant from a portion to which the first inclined upstream channel portion is connected, and is larger than the inner diameter of the first inclined upstream channel portion. 10. The connection device according to claim 9, wherein the inner diameter of the downstream side of the flow of the coolant is larger than the inner diameter of the second inclined upstream flow path portion with respect to the portion to which the upstream flow path portion is connected. The refrigeration cycle device is applied to a vehicle air conditioner, and includes a compressor (12) that compresses the sucked refrigerant and discharges it, and a driver's seat that uses the refrigerant discharged from the compressor (12) as a heat source. A heating unit (13, 30) for heating air blown to a first target space provided and a second target space different from the first target space; a first air-conditioning heat exchanger (14a) for cooling the blown air blown into the first target space before being heated by the heating section; a second air conditioning heat exchanger (14b) for cooling the blast air blown out to the second target space before being heated by the second air conditioning heat exchanger (14b); A cooling unit (16, 40) that cools the object to be cooled,
The plurality of inflow pipes include a first air conditioning inflow pipe (11d) in which the refrigerant flowing out from the first air conditioning heat exchanger flows, and a second air conditioning inflow pipe in which the refrigerant flowing out from the second air conditioning heat exchanger flows. (11e), and a cooling section inflow pipe (11b) through which the refrigerant flowing out from the cooling section flows,
The outflow pipe is a compressor outflow pipe (11c) that guides refrigerant to the compressor,
The serial upstream channel portion is connected to the first air conditioning inflow pipe,
The first inclined upstream channel portion is connected to the cooling portion inflow pipe,
The second inclined upstream channel portion is connected to the second air conditioning inflow pipe,
The connection device according to claim 9 or 10, wherein the downstream flow path portion is connected to the compressor outflow pipe. The second target space is a space in which a rear seat is provided,
The object to be cooled is a battery that supplies electric power for driving the vehicle,
12. The connection device according to claim 11, wherein the first inclined upstream channel portion merges with the downstream channel portion on the refrigerant flow upstream side of the second inclined upstream channel portion. The refrigeration cycle device circulates a refrigerant mixed with oil,
By switching the refrigerant circuit in which the refrigerant circulates, the operation mode of the refrigeration cycle device is changed from the operation mode in which the refrigerant flows through all of the plurality of inflow pipes to the operation mode in which the refrigerant flows through at least one of the plurality of inflow pipes. switchable to and from a no-flow mode of operation,
8, wherein the most downstream side of the refrigerant flow of the downstream channel portion is provided vertically above a refrigerant suction port (12a) through which the refrigerant is sucked into the compressor. 13. The connection device according to 11 or 12. 14. The downstream channel portion of any one of claims 1 to 13, wherein the most downstream side of the refrigerant flow of the downstream channel portion is provided vertically lower than the most upstream side of the refrigerant flow of the upstream channel portion. A connection device according to any one of the preceding claims. The inner diameter of the upstream channel portion is formed to have a size corresponding to the most downstream portion of the refrigerant flow of the inflow pipe to be connected,
15. Any one of claims 1 to 14, wherein the inner diameter of the downstream channel portion is larger than the inner diameter of the upstream channel portion and is formed in a size corresponding to the most upstream portion of the refrigerant flow of the outflow pipe. or 1. The connection device according to claim 1.

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