DE112021000868T5 - refrigeration cycle device - Google Patents

Abstract

A refrigeration cycle device has an evaporating pressure adjustment unit (20, 210) which is arranged downstream of a plurality of evaporating units (16, 18, 19) in a refrigerant flow and regulates a refrigerant evaporating pressure in the plurality of evaporating units. The plurality of evaporation units (16, 18, 19) has at least three evaporation units. One of the plurality of evaporating units (16, 18, 19) is defined as a first evaporating unit and another evaporating unit is defined as a second evaporating unit. The evaporating pressure adjustment unit (20) is capable of regulating a refrigerant evaporating pressure in the first evaporating unit to either a higher value or a lower value than a refrigerant evaporating pressure in the second evaporating unit.

Description

Cross-reference to related application

This application is based on Japanese Patent Application No. 2020-17177 , filed February 4, 2022, the disclosure of which is hereby incorporated by reference into this application.

technical field

The present disclosure relates to a refrigeration cycle device having evaporation units connected in parallel with each other with respect to a flow of refrigerant.

State of the art

Conventionally, Patent Document 1 discloses a refrigeration cycle device applied to a vehicle air conditioner. The refrigeration cycle device disclosed in Patent Document 1 has a plurality of heat exchangers that work (function, act) as evaporation units that evaporate refrigerant, and is configured to be capable of switching a refrigerant cycle. In a dehumidification and heating mode for dehumidifying and heating a vehicle cabin, the refrigerant circuit is switched to a refrigerant circuit in which an outdoor heat exchanger and an indoor evaporator, which are heat exchangers that work (function, act) as evaporating units, are connected in parallel to form a refrigerant flow.

The outdoor heat exchanger in the dehumidification and heating mode exchanges heat between the refrigerant and the outside air to evaporate the refrigerant. The indoor evaporator in the dehumidifying and heating mode exchanges heat between the refrigerant and a blown air blown into the vehicle cabin to evaporate the refrigerant. The refrigeration cycle device disclosed in Patent Document 1 further includes an evaporating pressure adjustment valve (a constant pressure valve in Patent Document 1). The evaporating pressure adjusting valve is a mechanically variable throttling device that is disposed on the downstream side of the indoor evaporator in the refrigerant flow and maintains the refrigerant evaporating pressure in the indoor evaporator at a predetermined reference value or greater.

As a result, in the refrigeration cycle device disclosed in Patent Document 1, in the dehumidifying and heating mode, the refrigerant evaporation temperature in the outdoor heat exchanger is reduced to be lower than an outside air temperature while the refrigerant evaporation temperature in the indoor evaporator is kept to be the same as or higher than the temperature at which the indoor evaporator can be prevented from being frosted. That is, in the refrigeration cycle device disclosed in Patent Document 1, the refrigerant is evaporated at different/different temperatures in the outdoor heat exchanger and the indoor evaporator by using the compression work of the evaporation pressure adjustment valve in the dehumidifying and heating mode.

Prior Art Documents

patent documents

Patent Document 1: JP 2012-225637 A

Summary of the Invention

In recent years, with the spread of electric vehicles and the like, there is an increased demand to cool a new cooling target such as a battery or other in-vehicle devices by using a refrigeration cycle device applied to a vehicle air conditioner. Therefore, it is conceivable that the evaporating unit for cooling the new cooling target is added to the refrigeration cycle device disclosed in Patent Document 1, and the refrigerant evaporating temperature in each evaporating unit is controlled to appropriately cool each cooling target.

However, the amount of self-heating (self-heating) of the cooling target such as a battery changes depending on an operation state. For this reason, the appropriate refrigerant evaporation temperature in the evaporating unit for cooling the cooling target such as a battery also changes depending on the operating state of the cooling target. For example, the appropriate refrigerant evaporating temperature in the evaporating unit for cooling the battery changes to a value higher than or lower than the refrigerant evaporating temperature in the indoor evaporator depending on the operational state of the battery.

In the refrigeration cycle device disclosed in Patent Document 1, the refrigerant evaporating temperatures of the two evaporating units connected in parallel are set to different/different temperatures by using the decompression work of the mechanical evaporating pressure adjustment valve. In such a configuration, the refrigerant evaporating temperature in an evaporating unit (for example, in the indoor unit evaporator in Patent Document 1) must not be lower than the refrigerant evaporating temperature in the other evaporating unit (for example, in the outdoor evaporator in Patent Document 1).

In order to regulate the refrigerant evaporating temperatures in all the evaporating units, it is conceivable that an individual electric evaporating pressure adjusting valve is arranged at the downstream side of each evaporating unit in the refrigerant flow to appropriately regulate the throttle opening of each evaporating pressure adjusting valve. However, when the individual evaporating pressure adjustment valve is arranged at the downstream side of each evaporating unit in the refrigerant flow, the cycle configuration of the entire refrigeration cycle device becomes complicated or large.

In view of this, an object of the present disclosure is to provide a refrigeration cycle device capable of appropriately regulating a refrigerant evaporating temperature in a plurality of evaporating units connected in parallel with each other with respect to a refrigerant flow, without reducing a refrigerant evaporating temperature in another evaporation unit is affected.

Another object of the present disclosure is to provide a refrigeration cycle device capable of appropriately regulating refrigerant evaporating temperatures in a plurality of evaporating units connected in parallel with each other with respect to refrigerant flow without making a cycle configuration complicated or larger .

In order to achieve the object, according to a first aspect of the present disclosure, a refrigeration cycle device includes: a plurality of evaporation units, an evaporation pressure adjustment unit, and a refrigerant cycle switching unit. The plurality of evaporation units causes a refrigerant to evaporate. The evaporating pressure adjustment unit is arranged on a downstream side of the plurality of evaporating units in a refrigerant flow, and regulates a refrigerant evaporating pressure in the plurality of evaporating units. The refrigerant cycle switching unit switches a cycle.

The plurality of evaporation units has at least three evaporation units. One of the plurality of evaporating units is defined as a first evaporating unit and another evaporating unit is defined as a second evaporating unit.

The refrigerant cycle switching unit switches a refrigerant cycle in which the first evaporating unit and the second evaporating unit are connected in parallel to flow refrigerant when the refrigerant is evaporated in the first evaporating unit and the second evaporating unit. The evaporating pressure adjustment unit is capable of regulating a refrigerant evaporating pressure in the first evaporating unit to either a higher value or a lower value than a refrigerant evaporating pressure in the second refrigerant evaporating unit.

Accordingly, the refrigerant cycle switching unit can connect two evaporating units of the three or more evaporating units in parallel with each other with respect to refrigerant flow. The evaporating pressure adjustment unit may regulate the refrigerant evaporating pressure in the first evaporating unit to be either higher or lower than the refrigerant evaporating pressure in the second evaporating unit.

Therefore, the refrigeration cycle device can be provided in which the refrigerant evaporating temperature in one of a plurality of evaporating units connected in parallel with each other with respect to the refrigerant flow can be appropriately regulated without affecting the refrigerant evaporating temperature in another evaporating unit.

According to a second aspect of the present disclosure, a refrigeration cycle device includes a plurality of evaporating units and an evaporating pressure adjustment unit. The plurality of evaporation units evaporates a refrigerant. The evaporating pressure adjustment unit is arranged on a downstream side of the plurality of evaporating units in a refrigerant flow, and regulates a refrigerant evaporating pressure in the plurality of evaporating units.

The evaporating units are connected in parallel to each other with respect to refrigerant flow. One of the plurality of evaporating units is defined as a first evaporating unit and another evaporating unit is defined as a second evaporating unit.

The evaporating pressure adjustment unit is designed to set a refrigerant evaporating pressure in the first evaporating unit to either to regulate a higher value or a lower value than a refrigerant evaporating pressure in the second evaporating unit.

The evaporation pressure adjustment unit includes a single opening regulation unit that regulates passage cross-sectional areas of a plurality of refrigerant passages in which the refrigerant flowing out from one of the plurality of evaporating units flows respectively, and a drive unit that adjusts the opening regulation unit.

Therefore, the evaporating pressure adjustment unit can regulate the refrigerant evaporating pressure in the first evaporating unit of the evaporating units connected in parallel to each other to either a higher value or a lower value than the refrigerant evaporating pressure in the second refrigerant evaporating unit. Furthermore, the evaporation pressure adjustment unit has the single opening regulation unit and the drive unit.

Accordingly, the refrigeration cycle device can be provided in which the refrigerant evaporation temperature in the evaporating units connected in parallel with each other can be appropriately regulated without incurring a complicated or enlarged cycle configuration.

character list

• 1 12 is an entire schematic configuration diagram of a refrigeration cycle device according to a first embodiment
• 2 12 is a front view of an integrated evaporation pressure adjustment valve according to the first embodiment.
• 3 is a view from an arrow III in 3 .
• 4 is a cross-sectional view taken along a line IV-IV in FIG 2 .
• 5 12 is a block diagram showing an electric control unit of the refrigeration cycle device according to the first embodiment.
• 6 12 is a front view of an integrated evaporation pressure adjustment valve according to a second embodiment.
• 7 is a view as seen from an arrow VII in 6 .
• 8th is a cross-sectional view taken along a line VIII-VIII in FIG 6 .
• 9 14 is a partially exploded perspective view of the integrated evaporation pressure adjustment valve according to the second embodiment.
• 10 12 is an explanatory diagram for explaining the shape of each communication hole in a valve body of the second embodiment.
• 11 12 is an entire schematic configuration diagram of a refrigeration cycle device according to a third embodiment.
• 12 14 is an entire schematic configuration diagram of a refrigeration cycle device according to a fourth embodiment.
• 13 12 is an entire schematic configuration diagram of a refrigeration cycle device according to another embodiment.

Description of the exemplary embodiments

Embodiments of the present disclosure are described below with reference to the drawings. In the embodiments, a part that corresponds to a matter described in a previous embodiment may be given the same reference numeral, and redundant explanation for the part may be omitted. When a part of a configuration is described in one embodiment, another previous embodiment can be applied to the other parts of the configuration. The parts can be combined even if it is not explicitly described that the parts can be combined. The embodiments can be partially combined even if it is not explicitly described that the embodiments can be combined, provided that their combination does not conflict with each other.

(First embodiment)

A first embodiment of the present disclosure is provided below with reference to FIG 1 until 5 described. In the present embodiment, a refrigeration cycle device 10 according to the present disclosure is applied to a vehicle air conditioner 1 mounted on an electric vehicle that receives a driving force for running from an electric motor. The vehicle air conditioner 1 not only performs air conditioning in a vehicle cabin, which is an air conditioning target space, but also has a function of cooling a battery 80, which is an in-vehicle device. That is, the vehicle air conditioner is an air conditioner having an in-vehicle device cooling function.

The battery 80 stores electric energy (electric power) supplied to an in-vehicle device such as an electric motor. The battery 80 is a secondary battery (a lithium ion battery in the present embodiment). The battery 80 is an assembled battery formed by stacking and arranging a plurality of battery cells and electrically connecting these battery cells in series or in parallel.

This type of battery generates heat during operation (that is, at the time of charging and discharging). The battery output is likely to decrease at a low temperature, and the battery is likely to deteriorate at a high temperature. Therefore, the temperature of the battery is required to be maintained within an appropriate temperature range (equal to or higher than 15°C and equal to or lower than 55°C in the present embodiment) in which the charging and discharging capacity of the battery is sufficient can be applied.

Therefore, in the vehicle air conditioner 1 , the battery 80 is cooled using cold generated by the refrigeration cycle device 10 . As in the overall design diagram of 1 As illustrated, the vehicle air conditioner 1 includes the refrigeration cycle device 10, an indoor air conditioning unit 30, a high-temperature-side heat-medium circuit 40, a low-temperature-side heat-medium circuit 50, and the like.

In order to carry out air conditioning in the vehicle cabin, the refrigeration cycle device 10 cools the air blown into the vehicle cabin and heats a high-temperature-side heat medium circulating in the high-temperature-side heat-medium circuit 40 . Furthermore, in order to cool the battery 80 , the refrigeration cycle device 10 cools a low-temperature-side heat medium circulating in the low-temperature-side heat-medium circuit 50 . The refrigeration cycle device 10 can switch refrigerant cycle in accordance with various operation modes described below.

The refrigeration cycle device 10 uses HFO refrigerant (specifically, R1234yf) as a refrigerant. The refrigeration cycle device 10 forms a subcritical refrigeration cycle in which the refrigerant pressure at a high-pressure side does not exceed the critical pressure of the refrigerant. A refrigerant oil (particularly, PAG oil) for lubricating a compressor 11 of the refrigeration cycle device 10 is mixed in the refrigerant. A part of the refrigerant oil circulates in the refrigerant cycle device 10 together with the refrigerant.

The compressor 11 sucks, compresses, and discharges the refrigerant in the refrigerant cycle device 10 . The compressor 11 is arranged in a power unit chamber on a front side of the vehicle cabin. The drive unit chamber forms a space in which at least part of a drive device (e.g., an electric motor for driving) for outputting a drive force for running is arranged.

The compressor 11 is an electric compressor in which a compression mechanism having a fixed discharge capacity is rotatably driven by an electric motor. The rotational speed (ie, the refrigerant discharge capacity) of the compressor 11 is controlled by a control signal output from a controller 60, which will be described later.

The inlet port side of a refrigerant passage of a water-refrigerant heat exchanger 12 is connected to the discharge port of the compressor 11 . The water-refrigerant heat exchanger 12 has a refrigerant passage in which the high-temperature refrigerant discharged from the compressor 11 flows and a water passage in which the high-temperature-side heat medium circulated in the high-temperature-side heat-medium circuit 40 flows. The water-refrigerant heat exchanger 12 is a heating heat exchanger that exchanges heat between the high-temperature refrigerant flowing in the refrigerant passage and the high-temperature side heating medium flowing in the water passage to heat the high-temperature side heating medium.

The inlet port side of a first three-way joint 13 a having three inlet and outlet ports communicating with each other is connected to the outlet port of the refrigerant passage in the water-refrigerant heat exchanger 12 . As such a three-way joint, a three-way joint formed by connecting a plurality of tubes, a three-way joint formed by providing a plurality of refrigerant passages in a metal block or a resin block, or the like can be used.

As described below, the refrigeration cycle device 10 further includes a second three-way joint 13b to a fourth three-way joint 13d. The basic configurations of the second three-way junction 13b to the fourth three-way junction junction 13d are the same as those of the first three-way junction 13a.

In the first three-way junction 13a to the fourth three-way junction 13d, when one of the three inlet and outlet ports is used as the inlet port and two are used as the outlet ports, the junctions act (function) as branch parts in which the flow of the refrigerant, the flowing from an inlet port is branched. When two of the three inlet and outlet ports are used as the inlet ports and one is used as the outlet port, the junctions function as merging parts in which the flows in the refrigerant chamber flowing from the two inlet ports are merged.

The inlet port side of a heating expansion valve 14a is connected to an outlet port of the first three-way joint 13a. An inlet port side of the second three-way joint 13b is connected to the other outlet port of the first three-way joint 13a through a bypass passage 23a. A high-pressure opening/closing valve 15a is arranged in the bypass passage 23a.

The high-pressure opening/closing valve 15a is an electromagnetic valve that opens and closes a refrigerant passage connecting the other outlet port side of the first three-way joint 13a and the one inlet port side of the second three-way joint 13b. The opening and closing operation of the high-pressure opening/closing valve 15 a is controlled by a control voltage output from the control device 60 .

The refrigeration cycle device 10 further includes a low-pressure opening/closing valve 15b described below. The basic configuration of the low-pressure opening/closing valve 15b is the same as that of the high-pressure opening/closing valve 15a. The high-pressure opening/closing valve 15a and the low-pressure opening/closing valve 15b can switch the refrigerant cycle in each operation mode by opening and closing the refrigerant passage. Therefore, the high-pressure opening/closing valve 15a and the low-pressure opening/closing valve 15b are refrigerant cycle switching units that switch the refrigerant cycle.

The heating expansion valve 14a is a heating decompression unit that decompresses the high-pressure refrigerant flowing out of the refrigerant passage of the water-refrigerant heat exchanger 12 and regulates the flow rate (the mass flow rate) of the refrigerant flowing to the downstream side in an outdoor air heating mode or the like, which will be described below is.

The heating expansion valve 14a is an electric variable throttle device having a valve body configured to be able to change a throttle opening and an electric actuator changing the opening of the valve body. The operation of the heating expansion valve 14a is controlled by a control signal (control pulse) output from the control device 60 .

The refrigeration cycle device 10 further includes a cabin refrigeration expansion valve 14b and a device refrigeration expansion valve 14c, which will be described later. The basic configurations of the cabin cooling expansion valve 14b and the device cooling expansion valve 14c are the same as those of the heating expansion valve 14a.

The heating expansion valve 14a, the cabin cooling expansion valve 14b and the device cooling expansion valve 14c have a full opening function, that is, they function as a simple refrigerant passage without exerting a flow rate regulation effect and a refrigerant decompression effect by fully opening the valve opening. Furthermore, the heating expansion valve 14a, the cabin cooling expansion valve 14b, and the device cooling expansion valve 14c have a full-closing function of closing the refrigerant passage by fully closing the valve opening.

Therefore, the heating expansion valve 14a, the cabin cooling expansion valve 14b, and the device cooling expansion valve 14c function (work, act) as a blocking unit that blocks the flow of refrigerant into the evaporating unit connected to the downstream side of each of the heating expansion valve 14a, the cabin cooling expansion valve 14b, and the device cooling expansion valve 14c is connected. Needless to say, the heating expansion valve 14a and the like can be formed by a combination of a variable throttle mechanism that does not have the full-closing function and an opening/closing valve. In this case, the opening/closing valve works (functions, acts) as a blocking unit.

The refrigerant inlet port side of an outdoor heat exchanger 16 is connected to the outlet port of the heating expansion valve 14a. The outdoor heat exchanger 16 is a heat exchanger that exchanges heat between the refrigerant flowing out from the heating expansion valve 14a and the outdoor air flowing through a cooling fan (not shown asked) is blown, exchanges. The outdoor heat exchanger 16 is arranged on the front side of the drive unit chamber. As a result, a running air can be applied to the outdoor heat exchanger 16 during running of the vehicle.

In an operation mode in which the temperature of the refrigerant flowing inside is higher than the outside air temperature as in a cooling mode described below, the outdoor heat exchanger 16 functions (operates, acts) as a condensing unit, the heat of the refrigerant to the outside air emits to condense the refrigerant. In an operation mode in which the temperature of the refrigerant flowing inside is lower than the outside air temperature as in an outside air heating mode described below, the outdoor heat exchanger 16 functions (operates, acts) as an evaporation unit that causes the refrigerant to heat the outside air to vaporize the refrigerant.

The inlet port side of the third three-way joint 13 c is connected to the refrigerant outlet port side of the outdoor heat exchanger 16 . A first inlet port 201a side of the integrated evaporation pressure adjustment valve 20 is connected to an outlet port of the third three-way joint 13c through a heating passage 22b. A detailed configuration of the integrated evaporation pressure adjustment valve 20 is described below. The low-pressure opening/closing valve 15b, which opens and closes the refrigerant passage, is arranged in the heating passage 22b.

The other inlet port side of the second three-way joint 13b is connected to the other outlet port side of the third three-way joint 13c. A check valve 17 is arranged in the refrigerant passage connecting the other outlet port side of the third three-way joint 13c and the other inlet port side of the second three-way joint 13b. The check valve 17 allows the refrigerant to flow from the third three-way junction 13c side to the second three-way junction 13b side and prevents the refrigerant from flowing from the second three-way junction 13b side to the third three-way junction 13c side.

The inlet port side of the fourth three-way joint 13d is connected to the outlet port side of the second three-way joint 13b. The inlet port side of the cabin cooling expansion valve 14b is connected to an outlet port of the fourth three-way joint 13d. The inlet port side of the device cooling expansion valve 14c is connected to another outlet port of the fourth three-way joint 13d.

The cabin cooling expansion valve 14b is a cooling decompression unit that decompresses the refrigerant that flows from the outdoor heat exchanger 16 and regulates the flow rate of the refrigerant that flows to the downstream side in an operation mode for cooling a blown air like the cooling mode described below.

The refrigerant inlet port side of an indoor evaporator 18 is connected to the outlet port of the cabin cooling expansion valve 14b. The indoor evaporator 18 is arranged in a casing 31 of the indoor air conditioning unit 30, which will be described later, the indoor evaporator 18 is an evaporation unit that heats between the low-pressure refrigerant decompressed by the cabin cooling expansion means 14b and the blown air blown by an indoor fan 32 , exchanges to vaporize the low-pressure refrigerant. A second inlet port 201 b side of the integrated evaporation pressure adjustment valve 20 is connected to the refrigerant outlet port of the indoor evaporator 18 .

The device cooling expansion valve 14c is a cooling decompression unit that decompresses the refrigerant flowing out of an outdoor heat exchanger 16 and regulates the flow rate of the refrigerant that flows to the downstream side in an operation mode for cooling the battery 80 as in a battery cooling mode described below .

The inlet port side of a refrigerant passage in a radiator 19 is connected to the outlet port of the device cooling expansion valve 14c. The radiator 19 has a refrigerant passage in which the low-pressure refrigerant decompressed by the device cooling expansion valve 14c flows, and a water passage in which the low-temperature-side heat medium circulated in the low-temperature-side heat-medium circuit 50 flows. The radiator 19 is a cooling heat exchange unit that exchanges heat between the low-pressure refrigerant flowing in the refrigerant passage and the low-temperature side heating medium flowing in the water passage to evaporate the low-pressure refrigerant. Consequently, the cooler 19 is an evaporation unit.

The side of a third inlet port 201c of the integrated evaporation pressure adjuster valve 20 is connected to the outlet port of the refrigerant passage in the radiator 19 . A detailed design of the integrated evaporation pressure adjustment valve 20 is given below with reference to FIG 2 until 4 described.

The integrated evaporating pressure adjustment valve 20 is an evaporating pressure adjustment unit that is arranged on the downstream side of a plurality of (three in the present embodiment) evaporating units such as the outdoor heat exchanger 16, the indoor evaporator 18, and the cooler 19 in the refrigerant flow, and is capable of to simultaneously regulate the refrigerant evaporation pressures in the plurality of evaporation units.

In other words, the integrated evaporating pressure adjustment valve 20 is a variable throttle device capable of decompressing each of the refrigerants flowing out from the plurality of evaporating units. As a result, the refrigerant evaporating pressure in the evaporating unit connected to the upstream side can be increased as the decompression amount of the refrigerant in the integrated evaporating pressure adjustment valve 20 increases.

The integrated evaporation pressure adjustment valve 20 has a body 201 , a valve body 202 and a drive unit 203 . The body 201 is a bottomed cylindrical member made of metal. The body 201 forms an outer shell of the integrated evaporation pressure adjustment valve 20 and further forms a columnar inner space therein.

Three inlet ports, that is, the first inlet port 201 a , the second inlet port 201 b , and the third inlet port 201 c , through which the refrigerant flows into the interior, are formed on the cylinder side surface of the body 201 . As in 3 and 4 1, the three intake ports are formed at equal angular intervals (at intervals of 120° in the present embodiments) as viewed from the central axis direction of the interior.

The three inlet ports, that is, the first inlet port 201a, the second inlet port 201b, and the third inlet port 201c form inlet ports of the refrigerant passages through which the refrigerants emitted from the outdoor heat exchanger 16, the indoor evaporator 18, and the radiator 19, which are the evaporation units , flow out, stream.

As in 2 As shown, the drive unit 203 is arranged on one end side of the body 201 in the central axis direction. As in 2 until 4 1, an outlet port 201d through which the refrigerant flows from the internal space is formed in the center of the bottom surface of the body 201 on the other end side in the center axis direction.

The drive unit 203 is an electric actuator that moves the valve body 202 arranged in the interior of the body 201 around the central axis. The operation of the drive unit 203 is controlled by a control signal (control pulse) output from the control device 60 .

The valve body 202 is a columnar member made of metal. As in 4 As shown, the valve body 202 is accommodated in the interior space of the body 201 . The cross section of the valve body 201 is formed in a fan shape as viewed from the central axis device. The central axis of the fan-shaped cross section of the valve body 202 is coaxial with the central axis of the interior of the body 201. The radius of the fan-shaped cross section of the valve body 202 is slightly smaller than the radius of the columnar interior of the body 201.

For this reason, as in 4 1, a seal member 205 that prevents the refrigerant from leaking from the gap between the valve body 202 and the body 201 is disposed on the inner peripheral side surface of the body 201. As shown in FIG. When the drive unit 203 moves the valve body 202 about the central axis, the outer peripheral side surface of the arcuate cross section of the valve body 202 slides on the sealing member 205.

The central angle of the fan shape of the valve body 202 is formed to be about 80° to 110°. When the drive unit 203 moves the valve body 202, each of the first inlet port 201a, the second inlet port 201b and the third inlet port 201c can be half opened or fully closed by the outer peripheral side surface of the arcuate cross section of the valve body 202. Then the remaining two ports can be fully opened. The half-open inlet port functions (works, acts) as a throttle (orifice) to exert a refrigerant pressure decompression action.

The valve body 202 can fully open all of the first inlet port 201a, the second inlet port 201b, and the third inlet port 201c. The valve body 202 is a single opening regulation unit having passage cross-sectional areas (e.g Opening areas of the first inlet port 201a, the second inlet port 201b and the third inlet port 201c) of the refrigerant passages in which the refrigerants flowing out from the evaporating units flow are regulated.

Each of the first inlet port 201a to the third inlet port 201c has a reed valve (not shown) for preventing the refrigerant from flowing from the interior side of the body 201 to the plurality of evaporation units side. That is, the integrated evaporation pressure adjustment valve 20 has a reverse flow prevention function of preventing the refrigerant from flowing from the outlet port 201d side to the plurality of evaporation units side.

The function of the integrated evaporation pressure adjustment valve 20 is described below. First, one of the outdoor heat exchanger 16, the indoor evaporator 18, and the cooler 19 is defined as a first evaporating unit, and another one of them is defined as a second evaporating unit. At this time, the integrated evaporation pressure adjustment valve 20 has a first function to regulate the refrigerant evaporation pressure in the first evaporating unit to be either higher or lower than the refrigerant evaporating pressure in the second evaporating unit by moving the valve body 202 .

The first function is described below by taking an example of an operation mode in which the outdoor heat exchanger 16 and the indoor evaporator 18 functioning (working, acting) as evaporating units are connected in parallel to a refrigerant flow as in a parallel dehumidifying mode described below. In this example, the outdoor heat exchanger 16 is defined as the first evaporating unit, and the indoor evaporator 18 is defined as the second evaporating unit.

First, it is assumed that the drive unit 203 moves the valve body 202 to a position where the second intake port 201b is half open as in the sectional view of FIG 4 is shown. In this case, the refrigerant flowing out from the outdoor heat exchanger 16 flows into the interior via the first inlet port 201a, which is fully open. The refrigerant that flows out from the indoor evaporator 18 is decompressed when passing through the second inlet port 201b that is half open, and flows into the indoor space.

As a result, in the integrated evaporation pressure adjustment valve 20, when the valve body 202 half opens the second inlet port 201b, the refrigerant evaporation pressure in the outdoor heat exchanger 16 functioning as the first evaporation unit can be regulated to a value lower than the refrigerant evaporation pressure in the indoor evaporator 18 , which functions as the second evaporation unit.

Hereinafter, it is assumed that the drive unit 203 moves the valve body 202 to a position where the first intake port 201a is half open. In this case, the refrigerant flowing out from the outdoor heat exchanger 16 is decompressed when flowing through the first inlet port 201a that is half open, and flows into the interior. The refrigerant flowing out from the indoor evaporator 18 flows into the indoor space via the second inlet port 201b, which is fully open.

As a result, in the integrated evaporation pressure adjustment valve 20, when the valve body 202 half opens the first inlet port 201a, the refrigerant evaporation pressure in the outdoor heat exchanger 16 functioning as the first evaporation unit can be regulated to a value higher than the refrigerant evaporation pressure in the indoor evaporator 18 , which functions as the second evaporation unit.

An evaporating unit different from the first evaporating unit and the second evaporating unit is defined as a third evaporating unit. At this time, the integrated evaporation pressure adjustment valve 20 has a second function to regulate the refrigerant evaporation pressure in the third evaporation unit to be equal to a low pressure of the refrigerant evaporation pressure in the first evaporation unit and the refrigerant evaporation pressure in the second evaporation unit.

The second function is described below, taking as an example an operation mode in which the outdoor heat exchanger 16, the indoor evaporator 18 and the chiller 19 functioning (working, acting) as evaporating units are connected in parallel to a refrigerant flow as in a parallel dehumidifying and waste heat recovery mode described below. In this example, the outdoor heat exchanger 16 is defined as the first evaporating unit, the indoor evaporator 18 is defined as the second evaporating unit, and the radiator 19 is defined as the third evaporating unit.

It is assumed that the drive unit 203 moves the valve body 202 to a position where the second intake port 201b is half open, as in the sectional view of FIG 4 is shown. In this case, as described above, the refrigerant evaporating pressure in the outdoor heat exchanger 16 which is the first evaporating unit is lower than the refrigerant evaporating pressure in the indoor evaporator 18 which is the second evaporating unit. The refrigerant flowing out from the radiator 19 flows into the interior via the third inlet port 201c, which is fully open.

As a result, in the integrated evaporation pressure adjustment valve 20, when the valve body 202 half opens the second inlet port 201b, the refrigerant evaporation pressure in the radiator 19 functioning as the third evaporation unit can be regulated to be the same as the refrigerant evaporation pressure in the outdoor heat exchanger 16 that works as the first evaporation unit. The same applies to each of the first to third evaporating units.

The inlet port side of an accumulator 21 is connected to the outlet port 201 d of the integrated evaporation pressure adjustment valve 20 . The accumulator 21 is a low-pressure side gas-liquid separator that separates (separates) low-pressure refrigerant into gas and liquid and stores the separated liquid-phase refrigerant as a surplus refrigerant in the cycle. The suction port side of the compressor 11 is connected to the gas-phase refrigerant outlet port of the accumulator 21 . That is, the compressor 11 sucks the refrigerant flowing out from the integrated evaporation pressure adjustment valve 20 via the accumulator 21 .

The high-temperature-side heat medium circuit 40 will be described below. The high-temperature-side heat cycle 40, which is 1 shown is a heat medium circulation circuit in which a high-temperature-side heat medium circulates. An ethylene glycol aqueous solution is used as the high-temperature-side heating medium. In the high-temperature-side heat-medium circuit 40, a water passage of the water-refrigerant heat exchanger 12, a high-temperature heat-medium pump 41, a heater core 42, and the like are arranged.

The high-temperature heat medium pump 41 is a water pump that pumps the high-side temperature heat medium to the inlet port side of the water passage in the water-refrigerant heat exchanger 12 . The high-temperature heat medium pump 41 is an electric pump whose rotation speed (ie, pumping capacity) is controlled by a control voltage output from the control device 60 .

The heat medium inlet port side of the heater core 42 is connected to the outlet port of the water passage in the water-refrigerant heat exchanger 12 . The heater core 42 is a heat exchanger that exchanges heat between the high-temperature-side heat medium heated by the water-refrigerant heat exchanger 12 and the blown air that passes through the indoor evaporator 18 to heat the blown air. The heater core 42 is arranged in the case 31 of the indoor air conditioning unit 30 . The suction port side of the high temperature heat medium pump 41 is connected to the heat medium outlet port of the heater core 42 .

Therefore, in the high-temperature-side heat-medium circuit 40, the high-temperature heat-medium pump 41 can regulate the amount of heat given off from the high-temperature-side heat medium to the blown air in the heater core 42 by regulating the flow rate of the high-temperature-side heat-medium flowing into the heater core 42, that is, the amount of heat of the blown air in the heater core 42 can be regulated.

That is, in the present embodiment, the individual components of the water-refrigerant heat exchanger 12 and the high-temperature-side heat medium circuit 40 constitute a heating unit that heats the blown air using the refrigerant discharged from the compressor 11 as a heat source.

The low-temperature-side heat medium circuit 50 will be described below. The low-temperature-side heat-medium circuit 50 is a heat-medium circulation circuit in which a low-temperature-side heat medium circulates. As the low-temperature-side heat medium, a fluid similar to the high-temperature-side heat medium can be used. In the low-temperature-side heat-medium circuit 50, a water passage of the radiator 19, a low-temperature heat-medium pump 51, a cooling water passage 80a of the battery 80, and the like are arranged.

The low-temperature heat-medium pump 51 is a water pump that pumps the low-temperature-side heat medium to the inlet port side of the water passage in the radiator 19 . The basic configuration of the low temperature heat medium pump 51 is the same as that of the high temperature heat medium pump 41. The inlet port side of the cooling water passage in the battery 80 is connected to the outlet port of the water passage of the radiator 19 .

The cooling water passage 80a is formed inside a battery case accommodating battery cells of the battery 80 . The cooling water passage 80a has a passage configuration in which passages are connected in parallel inside the battery case. As a result, the cooling water passage 80a can cool all the battery cells evenly. The suction port side of the low temperature heat medium pump 50 is connected to the outlet port of the cooling water passage 80a.

That is, in the present embodiment, the individual components of the radiator 19 and the low-temperature-side heat medium circuit 50 constitute a cooling unit that cools the battery 80 as a cooling target.

The interior air conditioning unit 30 is described below. The interior air conditioning unit 30 is a unit that blows blown air, which is controlled to an appropriate temperature to be blown into the vehicle cabin, to an appropriate place in the vehicle cabin. The interior air conditioning unit 30 is arranged inside an instrument panel on the frontmost side of the vehicle cabin.

In the indoor air conditioning unit 30, the indoor fan 32, the indoor evaporator 18, the refrigeration cycle device 10, the heater core 42 of the high temperature side heat medium circuit 40 and the like are housed in the case 31 forming the air passage of the blown air. The case 31 is formed of resin (e.g., polypropylene) that has a certain degree of elasticity and excellent strength.

An inside/outside air switching device 33 is arranged on the most upstream side of the housing 31 in a blast air flow. The inside/outside air switching device 33 switches between inside air (air inside the vehicle cabin) and outside air (air outside the vehicle cabin), and introduces the air into the case 31 . The operation of the inside-outside air switching device 33 is controlled by a control signal output from the control device 60 . The indoor fan 32 is arranged on the downstream side of the inside/outside air switching device 33 in the blown air flow. The indoor blower 32 blows air drawn in by the inside/outside air switching device 33 toward the vehicle cabin. The indoor fan 32 is an electric fan whose rotation speed (ie, blowing power) is controlled by a control voltage output from the control device 60 .

On the downstream side of the indoor fan 32 in the air blast flow, the indoor evaporator 18 and the heater core 42 are arranged in this order with respect to the air blast flow. That is, the indoor evaporator 18 is arranged on an upstream side of the heater core 42 in the blown air flow. Further, a cold air bypass passage 35 in which the blown air after passing through the indoor evaporator 18 flows to a downstream side while bypassing the heater core 42 is formed in the case 31 .

An air mix door 34 is arranged on the downstream side of the indoor evaporator 18 in the blown air flow and on the upstream side of the heater core 42 in the blown air flow. The air mix door 34 is an air volume ratio regulation unit that regulates an air volume ratio between the air volume of the blown air passing through the heater core 42 and the air volume of the blown air passing through the cold air bypass passage 35 in the blown air after passing through the indoor evaporator 18 .

The air mix door 34 is driven by an electric air mix door actuator. The operation of the air mix door electric actuator is controlled by a control signal output from the controller 60 .

A mixing space 36 is arranged on the downstream side of the heater core 42 and the cold air bypass passage 35 in the blown air flow. The mixing space 36 is a space in which the blown air that is heated by the heater core 42 and the blown air that passes through the cold air bypass passage 35 and is not heated are mixed. Furthermore, a plurality of openings (not shown) for blowing the blown air, which has been mixed in the mixing space 36 and subjected to temperature control, into the vehicle cabin are arranged at the most downstream portion of the housing 31 in the blown air flow.

The openings communicate with a plurality of exhaust ports formed in the vehicle cabin. As the plurality of blow-off ports, a face blow-off port, a foot blow-off port, and a defrost blow-off port are formed. The face blow-out port is a port that blows out blown air toward the upper body of an occupant. The foot blowing port is a port that has a blowing air blows out toward the occupant's feet. The defrost blowout port is a blowout port that blows out blown air toward a vehicle windshield.

The temperature of the conditioned air to be mixed in the mixing space 36 is regulated by the air mix door 34, which regulates the air volume ratio between the air volume passing through the heater core 42 and the air volume passing through the cold air bypass passage 35. As a result, the temperature of the blown air blown into the vehicle cabin from each of the blowout ports is regulated.

The structure of an electric control unit in the present embodiment will be described below. The control device 60 comprises a well-known microcomputer having a CPU, ROM, RAM and the like, and peripheral circuits. Various calculations and processes are executed based on an air conditioning control program stored in the ROM, and the operations of the various control target devices 11, 14a to 14c, 15a, 15b, 32, 33, 41 and 51 connected to the output side are controlled.

As in the block diagram of 5 shown are an inside air temperature sensor 61, an outside air temperature sensor 62, an insolation amount sensor 63, a first refrigerant temperature sensor 64a to a third refrigerant temperature sensor 64c, a discharge temperature sensor 64d, an evaporator temperature sensor 64f, a first refrigerant pressure sensor 65a to a fourth refrigerant pressure sensor 65d, a high temperature heat medium temperature sensor 66, a low-temperature heat medium temperature sensor 67, a battery temperature sensor 68, a conditioned air temperature sensor 69, and the like are connected to the input side of the control device 60. Detection signals from these sensor groups are input to the control device 60 .

The inside air temperature sensor 61 is an inside air temperature detection unit that detects a vehicle cabin temperature (inside air temperature) Tr. The outside air temperature sensor 62 is an outside air temperature detection unit that detects a vehicle outside temperature (outside air temperature) Tam. The solar radiation amount sensor 63 is a solar radiation amount detection unit that detects a solar radiation amount Ts with which the vehicle cabin is irradiated.

The first refrigerant temperature sensor 64a is a first refrigerant temperature detection unit that detects a first temperature T<b>1 of refrigerant flowing out from the water-refrigerant heat exchanger 12 . The second refrigerant temperature sensor 64b is a second refrigerant temperature detection unit that detects a second temperature T2 of refrigerant flowing out from the outdoor heat exchanger 16 . The third refrigerant temperature sensor 64c is a third refrigerant temperature detection unit that detects a third temperature T3 of refrigerant flowing out from the radiator.

The discharge temperature sensor 64 b is a discharge refrigerant temperature detection unit that detects a discharge temperature Td of refrigerant discharged from the compressor 11 . The evaporator temperature sensor 64f is an evaporator temperature detection unit that detects a refrigerant evaporation temperature (evaporator temperature) Tefin in the indoor evaporator 18 . Specifically, the evaporator temperature sensor 64f of the present embodiment detects the heat exchange fin temperature (heat exchange fin temperature) of the indoor evaporator 18.

The first refrigerant pressure sensor 65a is a first refrigerant pressure detection unit that detects a first pressure P<b>1 of refrigerant flowing out from a water-refrigerant heat exchanger 12 . The second refrigerant temperature sensor 64 b is a second refrigerant pressure detection unit that detects a second pressure P2 of refrigerant flowing out from an outdoor heat exchanger 16 . The third refrigerant pressure sensor 65c is a third refrigerant pressure detection unit that detects a third pressure P3 of refrigerant flowing out from a radiator 19 . The fourth refrigerant pressure sensor 65d is a fourth refrigerant pressure detection unit that detects a fourth pressure P4 of the refrigerant that flows out from the indoor evaporator 18 .

The high-temperature heat-medium temperature sensor 66 is a high-temperature-side heat-medium temperature detection unit that detects a high-temperature-side heat-medium temperature TWH that is the temperature of the high-temperature-side heat medium flowing out from the water passage of the water-refrigerant heat exchanger 12 . The low-temperature heat-medium temperature sensor 67 is a low-temperature-side heat-medium temperature detection unit that detects a low-temperature-side heat-medium temperature TWL that is the temperature of the low-temperature-side heat medium flowing out from the water passage of the radiator 19 .

The battery temperature sensor 68 is a battery temperature detection unit that detects a battery temperature TB (i.e., the temperature of the battery tery 80). The battery temperature sensor 68 of the present embodiment has a plurality of temperature sensors and detects temperatures at a plurality of portions of the battery 80. As a result, the control device 60 can also detect a temperature difference between the individual parts of the battery 80. Furthermore, the average value of the detection values of the plurality of temperature sensors is detected as the battery temperature TB.

The conditioned air temperature sensor 69 is a conditioned air temperature detection unit that detects a temperature TAV of the blown air blown into the vehicle cabin from the mixing space.

Furthermore, as in 5 1, an operation panel 70 located near the instrument panel on the front side of the vehicle cabin is connected to the input side of the control device 60, and operation signals from various operation switches provided on the operation panel 70 are input. Examples of the various operation switches provided on the operation panel 70 include an automatic switch, an air conditioner switch, an air volume setting switch, a temperature setting switch, and a blowing mode switch.

The automatic switch is an automatic control requesting unit that sets or cancels an automatic control operation of the vehicle air conditioner. The air conditioner switch is a cooling request unit that requests the indoor evaporator 18 to cool the blown air. The air volume setting switch is an air volume setting unit that manually sets the air volume of the indoor fan 32 . The temperature setting switch is a temperature setting unit that sets a target temperature Tset in the vehicle cabin. The blow mode switch is a blow mode switching unit that manually sets a blow mode.

Note that the control device 60 of the present embodiment is configured integrally with a control unit that controls various control target devices connected to the output side of the control device. A configuration (hardware and software) that controls the operation of each control target device forms a control unit that controls the operation of each control target device.

For example, the configuration of the control device 60 that controls the refrigerant discharge capacity of the compressor 11 (specifically, the rotational speed of the compressor 11) constitutes a compressor control unit 60a. The configuration for controlling the throttle openings of the heating expansion valve 14a, the cabin cooling expansion valve 14b and the device cooling expansion valve 14c constitutes an expansion valve control unit 60b.

The configuration for controlling the operations of the high pressure opening/closing valve 15a, the low pressure opening/closing valve 15b and the like forms an opening/closing valve control unit 60c. The configuration for controlling the operation of the integrated evaporating pressure adjustment angle 20 constitutes an evaporating pressure control unit 60d. The expansion valve control unit 60b, the opening/closing valve control unit 60c, and the like function(s) as a refrigerant cycle switching control unit that outputs a control signal when the refrigerant cycle is switched.

The operation of the vehicle air conditioner 1 of the present embodiment having the above configuration will be described below. As described above, the vehicle air conditioner 1 not only performs air conditioning in the vehicle cabin but also cools the battery 80. The refrigeration cycle device 10 can thus switch a refrigerant cycle to perform operation in various operation modes.

There are nine operation modes of the vehicle air conditioner 1, namely (1) cooling mode, (2) cooling and battery cooling mode, (3) serial dehumidifying mode, (4) parallel dehumidifying mode, (5) outside air heating mode, (6) outside air heating mode and waste heat recovery mode, (7) waste heat recovery and heating mode, (8) battery cooling mode, and (9) parallel dehumidification and waste heat recovery mode. These operation modes are switched by executing an air conditioning control program. The air conditioning control program is executed when the automatic switch of the operation panel 70 is turned on (ON) and the automatic control of the vehicle cabin is set. In the air conditioning control program, the detection signal of the sensor group and the operation signal of the operation panel 70 described above are read every predetermined period and the operation mode is switched.

Specifically, in the air conditioning control program, the operation mode is selected based on the outside air temperature Tam, a target blowing temperature TAO and the operation signal of the air conditioner switch on the operation panel 70 switched. The target blowing temperature TAO is a target temperature of the blowing air blown into the vehicle cabin.

Tset ist eine festgelegte Temperatur innerhalb der Fahrzeugkabine, die durch den Temperaturfestlegungsschalter festgelegt ist. Tr ist eine Temperatur innerhalb der Fahrzeugkabine, die durch den Innenluftsensor erfasst wird. Tam ist eine Temperatur außerhalb der Fahrzeugkabine, die durch den Außenluftsensor erfasst wird. Ts ist das Sonneneinstrahlungsausmaß, das durch den Sonneinstrahlungssensor erfasst wird. Kset, Kr, Kam und Ks sind Steuerungsverstärkungen und C ist eine Korrekturkonstante. Nachstehend ist der ausführliche Betrieb jedes Betriebsmodus beschrieben.The target blowing temperature TAO is calculated by the formula F1 below. $$\text{TAO}=\text{cheese}\times \text{Tset}-\text{kr}\times \text{Tr}-\text{Came}\times \text{tam}-\text{Ks}\times \text{ts}+\text{C}$$

Tset is a set temperature inside the vehicle cabin set by the temperature setting switch. Tr is a temperature inside the vehicle cabin detected by the inside air sensor. Tam is a temperature outside the vehicle cabin detected by the outside air sensor. Ts is the amount of solar radiation detected by the solar radiation sensor. Kset, Kr, Kam and Ks are control gains and C is a correction constant. The detailed operation of each operation mode is described below.

(1) Cooling mode

The cooling mode is an operation mode for cooling the vehicle cabin by blowing cooled blown air into the vehicle cabin without cooling the battery 80 .

The cooling mode is executed when the air conditioner switch is turned on, the outside air temperature Tam is higher than a predetermined reference outside air temperature KTam, and the target blowing temperature TAO is equal to or lower than a predetermined cooling reference temperature α1. Furthermore, the cooling mode is executed when it is determined that cooling of the battery 80 is not required.

Regarding the determination of whether the cooling of the battery 80 is required, it is determined that the cooling of the battery 80 is required when the battery temperature TB detected by the battery temperature sensor 68 is equal to or higher than a predetermined reference cooling temperature KTB (35°C in the present embodiment). In addition, when the battery temperature TB is lower than the reference cooling temperature KTB, it is determined that the cooling of the battery 80 is not required.

In addition, when the low-temperature-side heat-medium temperature TWL detected by the low-temperature heat-medium temperature sensor 67 is equal to or higher than a predetermined reference heat-medium temperature KTWL, it can be determined that the cooling of the battery 80 is required. When the low-temperature-side heat-medium temperature TWL is lower than the reference heat-medium temperature KTWL, it can be determined that the cooling of the temperature 80 is not required. The determination of whether or not cooling of the battery 80 is required is the same for the following modes of operation.

In the cooling mode, the controller 60 closes the high-pressure open/close valve 15a and also closes the low-pressure open/close valve 15b. The controller 60 places the heating expansion valve 14a in a fully open state, places the cabin cooling expansion valve 14b in a throttled state in which the refrigerant decompression work is performed, and places the device cooling expansion valve 14c in a fully closed state. The control device 60 controls the operation of the integrated evaporation pressure adjustment valve 20 such that at least the second inlet port 201b is fully open.

The control device 60 operates the high-temperature heat medium pump 41 to exert a predetermined pumping power.

Therefore, in the refrigeration cycle device 10, in the cooling mode, the refrigerant cycle is switched to a refrigerant cycle in which the refrigerant is introduced in the order of the compressor 11, the heat-refrigerant heat exchanger 12, the heating expansion valve 14a which is fully open, the outdoor heat exchanger 16, the check valve 17, of the cabin cooling expansion valve 14b, the indoor evaporator 18, the integrated evaporating pressure adjustment valve 20, the accumulator 21 and the compressor 11.

In the refrigerant cycle described above, the control device 60 appropriately controls the operations of various control target devices. For example, the controller 60 controls the rotational speed of the compressor such that the compressor temperature Tefin detected by the evaporator temperature sensor 64f approaches a target evaporator temperature TEO. The target evaporator temperature TEO is determined based on the target blowing temperature TAO with reference to a cooling mode control map stored in the control device 60 in advance.

In the cooling mode control map, the target evaporator temperature TEO is determined to increase as the target blowing temperature TAO increases. The target evaporator temperature TEO is set to a value in a range (specifically, a range of 1° C. or higher) in which the indoor evaporator 18 can be prevented from being frosted.

The control device 60 controls the throttle opening of the cabin cooling expansion valve 14b such that the supercooling degree SC1 of the refrigerant flowing into the cabin cooling expansion valve 14b approaches a target supercooling degree SCO1.

The degree of supercooling SC1 is determined using the second temperature T2 detected by the second refrigerant temperature sensor 64b and the second pressure P2 detected by the second refrigerant pressure sensor 65b. The target degree of supercooling SCO1 is determined based on the outside air temperature Tam with reference to the control map for a cooling mode stored in the control device 60 in advance. The target degree of supercooling SCO1 is determined such that the coefficient of performance (COP) of the cycle approaches the maximum value.

Regarding the opening of the air mix door 34, the controller 60 controls the operation of the electric air mix door actuator so that the blown air temperature TAV detected by the conditioned air temperature sensor 69 approaches the target blown air temperature TAO. In the cooling mode, since the target blowing temperature TAO is determined to be a relatively low value, the opening of the air mix door 34 is determined such that substantially the entire flow rate of the blowing air after passing through the indoor evaporator 18 passes through the cold air bypass passage 35.

Therefore, in the refrigeration cycle device 10, in the cooling mode, a vapor compression refrigerant cycle is formed in which the water-refrigerant heat exchanger 12 and the outdoor heat exchanger 16 function (work, function) as condensing units and the indoor evaporator 18 functions (work, function) as an evaporation unit. As a result, in the refrigeration cycle device 10 in the cooling mode, the high-temperature-side heat medium can be heated by the water-refrigerant heat exchanger 12 . The blown air can be cooled by the internal evaporator 18 .

In the high-temperature-side heat-medium circuit 40 in the cooling mode, the high-temperature-side heat-medium pumped by the high-temperature heat-medium pump 41 flows into the water-refrigerant heat exchanger 12. The high-temperature-side heat medium heated by the water-refrigerant heat exchanger 12 flows into the heater core 42.

In the interior air conditioning unit 30 in the cooling mode, part of the blown air cooled by the interior evaporator 18 is heated again by the heater core 42, and the blown air whose temperature has been controlled to approach the target blowing temperature TAO can be blown into the vehicle cabin . As a result, the vehicle cabin can be cooled.

(2) Cooling and battery cooling mode

The cooling and battery cooling mode is an operation mode for cooling the battery 80 and cooling the vehicle cabin by blowing cooled blast air into the vehicle cabin.

The cooling and battery cooling mode is executed when the air conditioner switch is turned on, the outside air temperature Tam is higher than the reference outside air temperature KTam, and the target blowing temperature TAO is equal to or lower than the cooling reference temperature α1. Furthermore, the cooling and battery cooling mode is executed when it is determined that cooling of the battery 80 is required.

In the cooling and battery cooling mode, the controller 60 closes the high-pressure open/close valve 15a and also closes the low-pressure open/close valve 15b. The controller 60 places the heating expansion means 14a in a fully open state, places the cabin cooling expansion valve 14b in a throttled state, and places the device cooling expansion valve 14c in a throttled state. The control device 60 controls the operation of the integrated evaporation pressure adjustment valve 20 such that one of the second inlet port 201b and the third inlet port 201c is half open (in a throttled state) or fully open, and the other of them is fully open.

The controller 60 operates the high-temperature heat medium pump 41 to exert the predetermined pumping power. The control device 60 operates the low-temperature heat medium pump 51 to exert the predetermined pumping power.

Therefore, in the refrigeration cycle device 10 in the cooling and battery cooling mode, the refrigerant circulates in the order of the compressor 11, the water-refrigerant heat exchanger 12, the heating expansion valve 14a which is fully open, the outdoor heat exchanger 16, the check valve 17, the fourth three-way junction 13b of the cabin cooling expansion valve 14b, the indoor evaporator 18, the integrated evaporating pressure adjusting valve 20, the receiver 21 and the compressor 11. Further, the refrigerant circulates in the order of the compressor 11, the heat-refrigerant heat exchanger 12, the heating expansion valve 14a which is fully open, the outdoor heat exchanger 16, check valve 17, fourth three-way junction 13d, device refrigeration expansion valve 14c, cooler 19, integrated evaporation pressure adjustment valve 20, accumulator 21 and compressor 11.

That is, in the refrigeration cycle device 10 in the cooling and battery cooling mode, a refrigerant branched at the fourth three-way junction 13d flows into the indoor evaporator 18 and the other refrigerant flows into the radiator 19. The refrigerant cycle is switched to a refrigerant cycle in which the Refrigerant flowing out from the indoor evaporator 18 and refrigerant flowing out from the radiator 19 are merged by the integrated evaporating pressure adjustment valve. That is, in the refrigeration cycle device 10 in the cooling and battery cooling mode, the refrigerant cycle is switched to a refrigerant cycle in which the indoor evaporator 18 and the radiator 19 are connected in parallel to flow refrigerant.

In the refrigerant cycle described above, the control device 60 controls appropriate operations of various control devices. For example, the control device 60 controls the throttle opening of the device cooling expansion valve 14c such that the superheat degree SHC on the outlet port side of the radiator 19 approaches a predetermined target superheat degree SHCO. The degree of superheat SHC is determined using the third temperature T3 detected by the third refrigerant temperature sensor 64c and the third pressure P3 detected by the third refrigerant pressure sensor 65c.

The controller 60 controls the operation of the integrated evaporation pressure adjustment valve 20 based on the throttle opening of the cabin cooling expansion valve 14b and the throttle opening of the device cooling expansion valve 14c.

Specifically, when the throttle opening of the cabin cooling expansion valve 14b is smaller than the throttle opening of the device cooling expansion valve 14c, the controller 60 controls the operation of the integrated evaporation pressure adjustment valve 20 to fully open the second inlet port 201b and to half open the third inlet port 201c (the third inlet port 201c in Fig to bring/set a throttled state). As a result, the refrigerant evaporating pressure in the indoor evaporator 18 is lower than the refrigerant evaporating pressure in the radiator 19.

The operating condition under which the throttle opening of the cabin cooling expansion valve 14b is smaller than the throttle opening of the device cooling expansion valve 14c is an operating condition under which the self-heating amount of the battery 80 is relatively small, as in the case of normal discharging of the battery 80. According to such an operating condition the refrigerant evaporating temperature in the radiator 19 is set to about 10°C while the refrigerant evaporating temperature in the indoor evaporator 18 is kept to about 1°C to prevent icing of the indoor evaporator.

When the throttle opening of the cabin cooling expansion valve 14b is larger than the throttle opening of the device cooling expansion valve 14c, the control device 60 controls the operation of the integrated evaporation pressure adjustment valve 20 to half open the second inlet port 201b (put the second inlet port 201b in a throttled state/set) and around fully open the third inlet port 201c. As a result, the refrigerant evaporating pressure 18 in the indoor evaporator 18 is higher than the refrigerant evaporating pressure in the radiator 19.

The operating condition under which the throttle opening of the cabin cooling expansion valve 14b is larger than the throttle opening of the device cooling expansion valve 14c is an operating condition under which the self-heating amount of the battery 80 is relatively large, as in the case of heavy-load discharge in which the battery 80 consumes a relatively large electric power ( electric current). According to such an operating condition, the refrigerant evaporation temperature in the radiator 19 is set to about -5°C while the refrigerant evaporation temperature in the indoor evaporator 18 is kept to about 1°C to prevent the indoor evaporator 18 from icing.

When the throttle opening of the cabin cooling expansion valve 14b is equal to the throttle opening of the device cooling expansion valve 14c, the controller 60 controls the operation of the integrated evaporation pressure adjustment valve 20 to fully open the second inlet port 201b and the third inlet port 201c. As a result, the refrigerant evaporating pressure in the outdoor evaporator 18 is the same as the refrigerant evaporating pressure in the indoor evaporator 18. The other control target devices are controlled in a same manner as in the cooling mode.

Therefore, in the refrigeration cycle device 10, in the cooling and battery cooling mode, a vapor compression refrigeration cycle is formed in which the water-refrigerant heat exchanger 12 and the outdoor heat exchanger 16 as the condensing unit th function (work, function) and the indoor evaporator 18 and the cooler 19 function (work, function) as evaporation units.

As a result, in the refrigeration cycle device 10 in the cooling and battery cooling mode, the high-temperature-side heat medium can be heated by the water-refrigerant heat exchanger 12 . The blown air can be cooled by the internal evaporator 18 . The low-temperature side heat medium can be cooled by the cooler 19 .

In the high temperature side heat medium circuit 40 in the cooling and battery cooling mode, the high temperature side heat medium pumped by the high temperature heat medium pump 41 flows into the water-refrigerant heat exchanger 12. The high temperature side heat medium heated by the water-refrigerant heat exchanger 12 flows into the heater core 32 .

In the low temperature side heat medium circuit 50 in the cooling and battery cooling mode, the low temperature side heat medium pumped by the low temperature heat medium pump 41 flows into the radiator 19. The low temperature side heat medium cooled by the radiator 19 flows into the cooling water passage 80a of the battery 80. As a result, the battery 80 can be cooled.

In the interior air conditioning unit 30 in the cooling and battery cooling mode, part of the blown air cooled by the interior evaporator 18 is heated again by the heater core 32, and the blown air whose temperature has been controlled (regulated) to approach the target blowing temperature TAO , are blown into the vehicle cabin. As a result, the vehicle cabin can be cooled.

In the cooling and battery cooling mode, the refrigerant evaporation pressure in the radiator 19 that functions (operates, acts) as the first evaporating unit can be set to either a higher value or a lower value than the refrigerant evaporation pressure in the indoor evaporator 18 that functions as the second evaporating unit ( works, acts) can be regulated by the action of the integrated evaporation pressure adjustment valve 20. Therefore, in the cooling and battery cooling mode, the temperature of the low-temperature side heating medium can be controlled (regulated) in a wide temperature range depending on the heat generation amount of the battery 80 or the like.

(3) Serial dehumidification mode

The serial dehumidification mode is an operation mode for dehumidifying and heating the vehicle cabin by reheating cooled and dehumidified blown air and blowing the reheated blown air into the vehicle cabin without cooling the battery 80 .

The serial dehumidification mode is executed when the air conditioner switch is turned on, the outside air temperature Tan is higher than the reference outside air temperature KTam, the target blowing temperature TAO is higher than the cooling reference temperature α1, and the target blowing temperature TAO is equal to or lower than a predetermined dehumidification reference temperature β1. Furthermore, the serial dehumidification mode is executed when it is determined that cooling of the battery 80 is not required.

In the serial dehumidifying mode, the controller 60 closes the high-pressure open/close valve 15a and also closes the low-pressure open/close valve 15b. The controller 60 places the heating expansion valve 14a in a throttled state, places the cabin expansion valve 14b in a throttled state, and places the device cooling expander 14c in a fully closed state. The control device 60 controls the operation of the integrated evaporation pressure adjustment valve 20 such that at least the second inlet port 201b is fully open.

The control device 60 operates the high-temperature heat medium pump 41 to exert the predetermined pumping power.

Therefore, in the refrigeration cycle device 10, in the serial dehumidifying mode, the refrigerant cycle is switched to a refrigerant cycle in which the refrigerant is mixed in the order of the compressor 11, the water-refrigerant heat exchanger 12, the heating expansion valve 14a, the outdoor heat exchanger 16, the check valve 17, the cabin cooling expansion valve 14b, of the indoor evaporator 18, the integrated evaporating pressure adjusting valve 20, the accumulator 21 and the compressor 11 is circulated.

In the refrigerant cycle described above, the control device 60 appropriately controls the operations of various control target devices. For example, the controller 60 controls the throttle opening of the heating expansion valve 14a and the throttle opening of the cabin expansion valve 14b based on the target blowing temperature TAO with reference to a serial dehumidification mode control map dus stored in the control device 60 in advance.

In the control map for a serial dehumidification mode, the throttle opening of the heating expansion valve 14a and the throttle opening of the cabin cooling expansion valve 14b are determined such that the throttle opening of the heating expansion valve 14a decreases and the throttle opening of the cabin cooling expansion valve 14b increases as the target blowing temperature TAO increases.

The other control target devices are controlled in the same manner as in the cooling mode.

Therefore, in the refrigeration cycle device 10 in the serial dehumidification mode, a vapor compression refrigeration cycle in which the water-refrigerant heat exchanger 12 functions (operates, acts) as a condensation unit and the indoor evaporator 18 functions (operates, acts) as an evaporation unit is formed.

When the saturation temperature of the refrigerant in the outdoor heat exchanger 18 is higher than the outdoor air temperature Tam, a cycle in which the outdoor heat exchanger 16 functions (operates, functions) as a condensing unit is formed. When the saturated refrigerant temperature of the outdoor heat exchanger 18 is lower than the outdoor air temperature Tan, a cycle is formed in which the outdoor heat exchanger 16 functions (operates, functions) as an evaporating unit.

As a result, in the refrigeration cycle device 10 in the serial dehumidification mode, the high-temperature-side heat medium can be heated by the water-refrigerant heat exchanger 12 . The blown air can be cooled and dehumidified by the internal evaporator 18 .

In the high-temperature-side heat-medium circuit 40 in the serial dehumidification mode, the high-temperature-side heat-medium pumped by the high-temperature heat-medium pump 41 flows into the water-refrigerant heat exchanger 12. The high-temperature-side heat medium heated by the water-refrigerant heat exchanger flows into the heater core.

In the indoor air conditioning unit 30 in the serial dehumidification mode, the blown air cooled and dehumidified by the indoor evaporator 18 is heated again by the heater core 42, and the blown air whose temperature has been regulated (regulated) to approach the target blown air temperature TAO in the vehicle cabin to be blown. As a result, the vehicle cabin can be dehumidified and heated.

In the series dehumidification mode, the throttle opening of the heating expander 14a decreases and the throttle opening of the cabin cooling expansion valve 14b increases as the target blowing temperature TAO increases. As a result, the amount of heat released from the refrigerant in the water-refrigerant heat exchanger 12 can be increased with the increase in the target blowing temperature TAO, thereby improving the ability to heat the blowing air in the heater core 42 .

(4) Parallel dehumidification mode

The parallel dehumidification mode is an operation mode for dehumidifying and heating the vehicle cabin by reheating cooled and dehumidified blown air and blowing the reheated blown air into the vehicle cabin without cooling the battery 80 .

The parallel dehumidifying mode is executed when the air conditioner switch is turned on, the outside air temperature Tan is higher than the reference outside air temperature KTam, and the target blowing temperature TAO is higher than the dehumidifying reference temperature β1. Furthermore, when it is determined that cooling of the battery 80 is not required, the parallel dehumidification mode is executed.

In the parallel dehumidifying mode, the controller 60 opens the high-pressure open/close valve 15a and also opens the low-pressure open/close valve 15b. The controller 60 places the heating expander 14a in a throttled state, places the cabin expansion valve 14b in a throttled state, and places the device cooling expander 14c in a fully closed state. The control device 60 controls the operation of the integrated evaporation pressure adjustment valve 20 such that one of the first inlet port 201a and the second inlet port 201b is half open (in a throttled state) or fully open and the other of them is fully open.

The controller 60 operates the high-temperature heat medium pump 41 to exert the predetermined pumping power.

Therefore, in the refrigeration cycle device 10, in the parallel dehumidifying mode, the refrigerant circulates in the order of the compressor 11, the water-refrigerant heat exchanger 12, the first three-way joint 13a, the heating expansion valve 14a, the outdoor heat exchanger 16, the heating passage 22b, the integrated evaporation pressure adjustment valve 20, the receiver 21 and the compressor 11. Further, the refrigerant circulates in the order of the compressor 11, the water-refrigerant heat exchanger 12, the first three-way junction 13a, the bypass passage 22a, the cabin cooling expansion valve 14b, the indoor evaporator 18 , the integrated evaporation pressure adjustment valve 20, the receiver 21 and the compressor 11.

That is, in the refrigeration cycle device 10 in the parallel dehumidifying mode, a refrigerant branched at the first three-way junction 13a flows into the outdoor heat exchanger 16 and the other refrigerant flows into the evaporator 18. The refrigerant cycle is switched to a refrigerant cycle in which the refrigerant, that flows out from the outdoor heat exchanger 16 and the refrigerant that flows out from the indoor evaporator 18 are merged by the integrated evaporating pressure adjustment valve 20 . That is, in the refrigeration cycle device 10 in the parallel dehumidifying mode, the refrigerant cycle is switched to a refrigerant cycle in which the outdoor heat exchanger 16 and the indoor evaporator 18 are connected in parallel to flow refrigerant.

In the refrigerant cycle described above, the control device 60 appropriately controls the operations of various control target devices. For example, the control device 60 controls the rotation speed of the compressor 11 such that the high-temperature-side heat-medium temperature TWH detected by the high-temperature heat-medium temperature sensor 66 approaches a predetermined high-temperature-side target heat-medium temperature TWHO.

For the heating expansion valve 14a and the cabin cooling expansion valve 14b, the controller 60 controls the opening ratio of the throttle opening of the cabin cooling expansion valve 14b to the throttle opening of the heating expansion valve 14a such that the superheat degree SHE of the refrigerant at the outlet port side of the indoor evaporator 18 approaches a predetermined target superheat degree SHEO. The degree of superheat SHE is determined using the evaporation temperature Tefin and the fourth pressure P4 detected by the fourth refrigerant expansion sensor 65d.

Specifically, when the superheat degree SHE is larger than the target superheat degree SHEO, the opening ratio of the throttle opening of the cabin cooling expander 14b to the throttle opening of the heating expander 14a is increased. When the superheat degree SHE is smaller than the target superheat degree SHEO, the opening ratio of the throttle opening of the cabin cooling expansion means 14b to the throttle opening of the heating expansion valve 14a is reduced.

The control device 60 controls the operation of the integrated evaporation pressure adjustment valve 20 such that the evaporator temperature Tefin approaches the target evaporator temperature TEO.

Specifically, when the evaporator temperature Tefin is lower than the target evaporator temperature TEO, the controller 60 controls the operation of the integrated evaporation pressure adjustment valve 20 to fully open the first inlet port 201a and to half open the second inlet port 201b (to move the second inlet port 201b into the throttled to bring/put into condition). As a result, the refrigerant evaporating pressure in the outdoor heat exchanger 16 is lower than the refrigerant evaporating pressure in the indoor evaporator 18.

The operating condition that the evaporator temperature Tefin is lower than the target evaporator temperature TEO is an operating condition that the target blowing temperature TAO increases and the ability to heat the blowing air is required to improve. According to such an operating condition, the refrigerant evaporating temperature in the outdoor heat exchanger 16 is set to be equal to or lower than the outside air temperature (e.g. -5°C), while the refrigerant evaporating temperature in the indoor evaporator 18 is kept at about 1°C to to prevent the indoor evaporator 18 from icing up.

When the evaporator temperature Tefin is higher than the target evaporator temperature TEO, the controller 60 controls the operation of the integrated evaporation pressure adjustment valve 20 to half open the first inlet port 201a (to bring the first inlet port 201a to the throttled state) and to open the second inlet port 201b to open fully. As a result, the refrigerant evaporation pressure in the outdoor heat exchanger 16 becomes/is higher than the refrigerant evaporation pressure in the evaporator 18.

The operating condition where the evaporator temperature Tefin is higher than the target evaporator temperature TEO is an operating condition where the target blowing temperature decreases and the ability to heat the blowing air decreases. According to such an operating condition, the refrigerant evaporation temperature in the outdoor evaporator 16 is set to be low to be lower than the outside temperature and to be higher than the refrigerant evaporating temperature in the indoor evaporator 18 while maintaining the refrigerant evaporating temperature in the indoor evaporator 18 at the target evaporating temperature TEO. The other control target devices are controlled in a similar manner as in the cooling mode.

Therefore, in the refrigeration cycle device 10, in the parallel dehumidification mode, a vapor compression cycle is formed in which the water-refrigerant heat exchanger 12 functions (works, functions) as a condensing unit and the outdoor evaporator 16 and the indoor evaporator 18 functions (works, functions) as evaporation units. As a result, in the refrigeration cycle device 10 in the parallel dehumidification mode, the high-temperature-side heat medium can be heated by the water-refrigerant heat exchanger 12 . The blown air can be cooled by the internal evaporator 18 .

In the high-temperature-side heat-medium circuit 40 in the parallel dehumidification mode, the high-temperature-side heat-medium pumped by the high-temperature heat-medium pump 41 flows into the water-refrigerant heat exchanger 12. The high-temperature-side heat medium heated by the water-refrigerant heat exchanger 12 flows into the heater core 42.

In the indoor air conditioning unit 60 in the parallel dehumidification mode, part of the blown air cooled and dehumidified by the indoor evaporator 18 is heated again by the heater core 42 and allows the blown air whose temperature has been controlled (regulated) to approach the target blowing temperature TAO , are blown into the vehicle cabin. As a result, the vehicle cabin can be dehumidified and heated.

In the parallel dehumidification mode, the refrigerant evaporating pressure in the outdoor heat exchanger 16 can be regulated to be either higher or lower than the refrigerant evaporating pressure in the indoor evaporator 18 by the action of the integrated evaporating pressure adjustment valve 20 .

Accordingly, when the target blowing temperature TAO increases, the refrigerant evaporating pressure in the outdoor heat exchanger 16 can be set to a value lower than the refrigerant evaporating pressure in the indoor evaporator 18. As a result, the amount of heat absorbed by the refrigerant from the outdoor air in the outdoor heat exchanger 16 will be increased more than that in the serial dehumidifying mode. The amount of heat that is released from the refrigerant to the high-temperature-side heat medium in the water-refrigerant heat exchanger 12 can be increased to improve the ability to heat the blown air in the heater core 42 .

In addition, when the target blowing temperature TAO decreases, the refrigerant evaporating pressure in the outdoor heat exchanger 16 can be set to a value higher than the refrigerant evaporating pressure in the indoor evaporator 18. As a result, the amount of heat carried by the refrigerant from the outdoor air through the outdoor heat exchanger 16 is recorded can be reduced. The amount of heat that is released from the refrigerant to the high-temperature-side heat medium in the water-refrigerant heat exchanger 12 can be reduced to lower the ability to heat the blown air in the heater core 42 .

As a result, in the parallel dehumidifying mode, the ability to heat the blown air in the heater core 42 can be controlled (regulated) in a wide (wide) range depending on the target blowing temperature TAO.

(5) Outdoor air heating mode

The outside air heating mode is an operation mode for heating the vehicle cabin by heating and blowing air blast into the vehicle cabin without cooling the battery 80 .

The outside air heating mode is executed when the air conditioner switch is not turned on and the target blowing temperature TAO is equal to or higher than a predetermined heating reference temperature γ1. Furthermore, the outside air heating mode is executed when it is determined that cooling of the battery 80 is not required.

In the outside-air heating mode, the controller 60 closes the high-pressure open/close valve 15a and opens the low-pressure open/close valve 15b. The controller 60 places the heating expansion valve 14a in a throttled state, places the cabin expansion valve in a closed state, and places the device cooling expansion valve 14c in a fully closed state. The control device 60 controls the operation of the integrated evaporation pressure adjustment valve 20 such that at least the first inlet port 201 is fully open.

The controller 60 operates the high-temperature heat medium pump 41 to exert the predetermined pumping power.

Therefore, in the refrigeration cycle device 10, in the outdoor air heating mode, the refrigerant cycle is switched to a refrigerant cycle in which the refrigerant is mixed in the order of the compressor 11, the water-refrigerant heat exchanger 12, the heating expansion valve 14a, the outdoor heat exchanger 16, the heating passage 22b, the integrated evaporation pressure adjustment valve 20, of the accumulator 22 and the compressor 11 is circulated.

In the refrigerant cycle described above, the control device 60 appropriately controls the operations of various control target devices. For example, the controller 60 controls the throttle opening of the heating expansion valve 14a such that the supercooling degree SC2 of the refrigerant flowing into the heating expansion valve 14a approaches a predetermined target supercooling degree SCO2 for an outdoor air heating mode. The degree of supercooling SC2 is determined using the first temperature T1 detected by the first refrigerant temperature sensor 64a and the first pressure P1 detected by the first refrigerant pressure sensor 65a. The other control target devices are controlled in a same manner as in the parallel dehumidifying mode.

Therefore, in the refrigeration cycle device 10 in the outdoor air heating mode, a vapor compression refrigerant cycle is formed in which the water refrigerant cycle 12 functions (operates, functions) as a condensation unit and the outdoor heat exchanger 16 functions (operates, functions) as an evaporation unit. As a result, in the refrigeration cycle device 10 in the outside-air heating mode, the high-temperature-side heat medium can be heated by the water-refrigerant heat exchanger.

In the high temperature side heat medium circuit 40 in the outside air heating mode, the high temperature side heat medium pumped by the high temperature heat pump 41 flows into the water-refrigerant heat exchanger 12. The high temperature side heat medium heated by the water-refrigerant heat exchanger 12 flows into the heater core 42.

In the interior air conditioning unit 30 in the outside air heating mode, the blown air heated by the heater core 42 can be blown into the vehicle cabin. As a result, the vehicle cabin can be heated.

(6) Outdoor air heating and waste heat recovery mode

The outside air heating and exhaust heat recovery mode is an operation mode for cooling the battery 80 and heating the vehicle cabin by heating and blowing air blast into the vehicle cabin. In other words, the outside air heating and waste heat recovery mode is for heating the blown air using heat received from the outside air and the battery 80 as a heat source.

The outdoor air heating and exhaust heat recovery mode is executed when the air conditioner switch is not turned on and the target blowing temperature TAO is equal to or higher than the predetermined heating reference temperature γ1. Furthermore, when it is determined that the cooling of the battery 80 is required, the outside air heating and waste heat recovery mode is executed.

In the outside-air heating and waste heat recovery mode, the controller 60 opens the high-pressure open/close valve 15a and also opens the low-pressure open/close valve 15b. The controller 60 places the heating expansion valve 14a in a throttled state, places the cabin cooling expansion valve 14b in a fully closed state, and places the device cooling expansion valve 14c in a throttled state. The control device 60 controls the operation of the integrated evaporation pressure adjustment valve 20 such that one of the first inlet port 201a and the third inlet port 201c is half open (in a throttled state) or fully open and the other of them is fully open.

The controller 60 operates the high-temperature heat medium pump 41 to exert the predetermined pumping power. The control device 60 operates the low-temperature heat medium pump 51 to exert the predetermined pumping power.

Therefore, in the refrigeration cycle device 10, in the outdoor air heating and waste heat recovery mode, the refrigerant circulates in the order of the compressor 11, the water-refrigerant heat exchanger 12, the first three-way junction 13a, the heating expansion valve 14a, the outdoor heat exchanger 16, the heating passage 22b, the integrated evaporating pressure adjustment valve 20, the receiver 21 and the compressor 11. Further, the refrigerant circulates in the order of the compressor 11, the water-refrigerant heat exchanger 12, the first three-way joint 13a, the bypass passage 22a, the device cooling expansion valve 14c, the chiller 19, the integrated evaporating pressure adjusting valve 20, the receiver 21 and the compressor 11.

That is, in the refrigeration cycle device 10 in the outdoor air heating and exhaust heat recovery mode, refrigerant charged at the first th three-way joint 13a branches off into the outdoor heat exchanger 16, and the other refrigerant flows into the radiator 19. The refrigerant cycle is switched to a refrigerant cycle in which the refrigerant flowing out from the outdoor heat exchanger 16 and the refrigerant flowing out from the radiator 19 are brought together by the integrated evaporation pressure adjustment valve 20. That is, in the refrigeration cycle device 10 in the outdoor air heating and exhaust heat recovery mode, the refrigerant cycle is switched to a refrigerant cycle in which the outdoor heat exchanger 16 and the radiator 19 are connected in parallel to a refrigerant flow.

In the refrigerant cycle described above, the control device 60 appropriately controls the operations of various control target devices. For the heating expansion valve 14a and the device cooling expansion valve 14c, the control valve 60 regulates (regulates) the opening ratio of the throttle opening of the device cooling expansion valve 14c to the throttle opening of the heating expansion valve 14a such that the superheat degree SHC of the refrigerant at the outlet port side of the radiator 19 approaches a target superheat degree SHCO.

Specifically, when the superheat degree SHC is larger than the target superheat degree SHCO, the gear ratio of the throttle opening of the device cooling expansion valve 14c to the throttle opening of the heating expansion valve 14a is increased. When the superheat degree SHC is smaller than the target superheat degree SHCO, the opening ratio of the throttle opening of the cabin cooling expansion valve 14c to the throttle opening of the heating expansion valve 14a is reduced.

The control device 60 controls the operation of the integrated evaporation pressure adjustment valve 20 based on the refrigerant evaporation temperature in the radiator 19. The third temperature T3 can be used as the refrigerant evaporation temperature in the radiator 19.

Specifically, when the refrigerant evaporation temperature in the radiator 19 is lower than a predetermined reference temperature, the controller 60 controls the operation of the integrated evaporation adjustment valve 20 to fully open the first inlet port 201a and to half open the third inlet port 201c (to open the third inlet port 201c into a throttled state). As a result, the refrigerant evaporating pressure in the outdoor heat exchanger 16 becomes/is lower than the refrigerant evaporating pressure in the radiator 19.

The operating condition under which the refrigerant evaporation temperature in the radiator 19 is lower than the reference temperature is an operating condition under which the ability to heat the blown air is improved by reducing the outside air temperature Tan. According to such an operating condition, the refrigerant evaporating temperature in the outdoor heat exchanger 16 is set to be equal to or lower than the outside air temperature (for example, about -10°C), while the refrigerant evaporating temperature in the radiator 19 is kept at about 0°C. to prevent excessive cooling of the battery 80.

When the refrigerant evaporation temperature in the radiator 19 is higher than the predetermined reference temperature, the controller 60 controls the operation of the integrated evaporation pressure adjustment valve 20 to half open the first inlet port 201a (to bring the first inlet port 201a in a throttled state) and third Inlet port 201c fully open. As a result, the refrigerant evaporating pressure in the outdoor heat exchanger 16 becomes/is higher than the refrigerant evaporating pressure in the radiator 19.

The operating condition under which the refrigerant evaporation temperature in the radiator 19 is higher than the reference temperature is an operating condition under which the vehicle cabin can be heated by using the waste heat of the battery 80 and the ability to heat the blown air is not required to be improved target. According to such an operating condition, the refrigerant evaporation temperature in the outdoor heat exchanger 16 is set to about 1°C while the refrigerant evaporation temperature in the radiator 19 is kept to about 0°C to prevent the outdoor heat exchanger 16 from icing. The other control target devices are controlled in a same manner as in the parallel dehumidifying mode.

Therefore, in the refrigeration cycle device 10 in the outdoor air heating and waste heat recovery mode, a vapor compression refrigeration cycle is formed in which the water-refrigerant heat exchanger 12 functions (operates, functions) as a condensation unit and the outdoor heat exchanger 16 and the radiator 19 functions (operates, functions) as evaporation units. As a result, in the refrigeration cycle device 10 in the outside-air heating and exhaust heat recovery mode, the high-temperature-side heating medium can be heated by the water-refrigerant heat exchanger 12 . The low-temperature side heat medium can be cooled by the cooler 19 .

In the high temperature side heat medium circuit 40 in the outdoor air heating and waste heat recovery mode, the high temperature side heat medium pumped by the high temperature heat medium pump 41 flows into the water-refrigerant heat exchanger 12. The high temperature side heat medium heated by the water-refrigerant heat exchanger 12 flows into the heater core 42 .

In the low-temperature-side heat-medium circuit 50 in the outdoor-air heating and exhaust-heat recovery mode, the low-temperature-side heat-medium pumped by the low-temperature heat-medium pump 51 flows into the radiator 19. The low-temperature-side heat medium cooled by the radiator 19 flows into the cooling water passage 80a of the battery 80. As a result, the battery 80 can be cooled. In other words, the low-temperature-side heat medium can absorb the waste heat from the battery 80 .

In the interior air conditioning unit 60 in the outside air heating and exhaust heat recovery mode, the blown air heated by the heater core 42 can be blown into the vehicle cabin. As a result, the vehicle cabin can be heated.

In the outdoor air heating and waste heat recovery mode, the refrigerant evaporating pressure in the outdoor heat exchanger 16 can be regulated to be either higher or lower than the refrigerant evaporating pressure in the radiator 19 by the action of the integrated evaporating pressure adjustment valve 20 .

As a result, when it is necessary to improve the ability to heat the blown air, the refrigerant evaporating pressure in the outdoor heat exchanger 16 can be set to a value lower than the refrigerant evaporating pressure in the radiator 19 without the refrigerant evaporating pressure in the radiator 19 changing becomes. As a result, the amount of heat absorbed by the refrigerant from the outside air in the outside air heat exchanger 16 can be increased.

The amount of heat released from the refrigerant to the high-temperature-side heat medium in the water-refrigerant heat exchanger 12 can be increased without changing the temperature of the low-temperature-side heat medium cooled by the radiator 19, thereby increasing the ability to heat the blown air in the heater core 42 is improved.

In addition, when it is necessary to reduce the ability to heat the blown air, the refrigerant evaporating pressure in the outdoor heat exchanger 16 can be set to a value higher than the refrigerant evaporating pressure in the radiator 19 without changing the refrigerant evaporating pressure in the radiator 19 . As a result, the amount of heat absorbed by the refrigerant from the outside air in the outside heat exchanger 16 can be reduced.

The amount of heat released from the refrigerant to the high-temperature-side heat medium in the water-refrigerant heat exchanger 12 can be reduced without reducing the temperature of the low-temperature-side heat medium cooled by the radiator 19, thereby increasing the ability to heat the blown air in the heater core 42 is decreased.

As a result, in the outdoor air heating and exhaust heat recovery mode, the ability to heat the blown air in the heater core 42 can be regulated in a wide range depending on the ability required to heat the blown air while appropriately cooling the battery 80 .

(7) Waste heat recovery and heating mode

The exhaust heat recovery and heating mode is an operation mode for cooling the battery 80 and heating the vehicle cabin by heating and blowing the blown air into the vehicle cabin. Specifically, the exhaust heat recovery and heating mode is an operation mode for heating the blown air using heat received from the battery 80 as a heat source.

The exhaust heat recovery and heating mode is executed when the air conditioner switch is not turned on and the target blowing temperature TAO is equal to or higher than the heating reference temperature y1. Furthermore, when it is determined that the cooling of the battery 80 is required, the exhaust heat recovery and heating mode is executed.

In the exhaust heat recovery and heating mode, the controller 60 opens the high-pressure open/close valve 15a and closes the low-pressure open/close valve 15b. The controller 60 places the heating expansion valve 14a in a fully closed state, places the cabin cooling expansion valve 14b in a fully closed state, and places the device cooling expansion valve 14c in a throttled state. The control device 60 controls the operation of the integrated evaporation pressure adjustment valve 20 such that at least the third inlet port 201c is fully open.

The controller 60 operates the high-temperature heat medium pump 41 to exert the predetermined pumping power. The control device 60 operates the low-temperature heat medium pump 51 to exert the predetermined pumping power.

Therefore, in the refrigeration cycle device 10, in the waste heat recovery and heating mode, the refrigerant cycle is switched to a refrigerant cycle in which the refrigerant is integrated in the order of the compressor 11, the water-refrigerant heat exchanger 12, the bypass passage 23a, the device cooling expansion valve 14c, the radiator 19, the Evaporation pressure adjustment valve 20, the accumulator 21 and the compressor 11 circulates.

In the refrigerant cycle described above, the control device 60 appropriately controls operations of various control target devices. For example, the control device 60 controls the throttle opening of the device cooling expansion valve 14c such that the supercooling degree SC3 of the refrigerant flowing into the device cooling expansion valve 14c approaches a target supercooling degree SCO3. The degree of supercooling SC3 is determined using the first temperature T1 and the first pressure P1.

The target degree of supercooling SCO3 is determined based on the high-temperature-side target heat-medium temperature TWHO with reference to an outside-air heating mode control map stored in the control device 60 in advance. The target degree of supercooling SCO3 is determined such that the COP approaches the maximum value. The other control target devices are controlled in the same manner as in the parallel dehumidifying mode.

Therefore, in the refrigeration cycle device 10 in the waste heat recovery and heating mode, a vapor compression refrigerant cycle is formed in which the water-refrigerant heat exchanger 12 functions (operates, functions) as a condensation unit and the radiator 19 functions (operates, functions) as an evaporation unit. As a result, in the refrigeration cycle device 10 in the outside-air heating mode, the high-temperature-side heat medium can be heated by the water-refrigerant heat exchanger 12 . The low-temperature side heat medium can be cooled by the cooler 19 .

In the high-temperature-side heat-medium cycle 40 in the waste heat recovery and heating mode, the high-temperature-side heat-medium pumped by the high-temperature heat-medium pump 41 flows into the water-refrigerant heat exchanger 12. The high-temperature-side heat medium heated by the water-refrigerant heat exchanger 12 flows into the heater core 42 .

In the low-temperature-side heat-medium circuit 50 in the exhaust heat recovery and heating mode, the low-temperature-side heat-medium pumped by the low-temperature heat-medium pump 51 flows into the radiator 19. The low-temperature-side heat medium cooled by the radiator 19 flows through the cooling water passage 80a of the battery 80. As a result, the battery 80 can be cooled. In other words, the low-temperature-side heat medium can absorb the waste heat from the battery 80 .

In the interior air conditioning unit 60 in the exhaust heat recovery and heating mode, the blown air heated by the heater core 42 can be blown into the vehicle cabin. As a result, the vehicle cabin can be heated.

(8) battery cooling mode

The battery cooling mode is an operation mode for cooling the battery 80 without performing air conditioning in the vehicle cabin. The battery cooling mode is executed when air conditioning is not required or when the air conditioner switch is not turned on and the target blowing temperature TAO is lower than the heating reference temperature y1. Furthermore, the battery cooling mode is executed when it is determined that cooling of the battery 80 is required.

In the battery cooling mode, the controller 60 closes the high-pressure open/close valve 15a and also closes the low-pressure open/close valve 15b. The controller 60 places the heating expansion valve 14a in a fully open state, places the cabin cooling expansion valve 14b in a fully closed state, and places the device cooling expansion valve 14c in a throttled state. The control device 60 controls the operation of the integrated evaporation pressure adjustment valve 20 such that at least the third inlet port 201c is fully open.

Furthermore, the controller 60 stops the high-temperature heat-medium pump 41. The controller 60 operates the low-temperature heat-medium pump 51 to exert the predetermined pumping power.

Therefore, in the refrigeration cycle device 10 in the battery cooling mode, the refrigeration cycle becomes closed is switched to a refrigeration cycle in which the refrigerant is changed in the order of the compressor 11, (the water-refrigerant heat exchanger 12), the heating expansion valve 14a which is fully open, the outdoor heat exchanger 16, the check valve 17, the device cooling expansion valve 14c, the chiller 19, the integrated Evaporation pressure adjustment valve 20, the accumulator 21 and the compressor 11 circulates.

In the refrigerant cycle described above, the control device 60 appropriately controls operations of various control target devices. For example, regarding the opening of the air mix door 34, the controller 60 controls the operation of an electric actuator for an air mix door to fully close an air passage on the heater core 42 side. The control device 60 stops the indoor fan 32. The other control target devices are controlled in a same manner as in the cooling mode.

Therefore, in the refrigeration cycle device 10 in the battery cooling mode, a vapor compression refrigeration cycle is formed in which the outdoor heat exchanger 16 functions (operates, functions) as a condensation unit and the radiator 19 functions (operates, functions) as an evaporation unit. As a result, in the refrigeration cycle device 10 in the battery cooling mode, the low-temperature side heat medium can be cooled by the radiator 19 .

In the low-temperature-side heat-medium circuit 50 in the battery cooling mode, the low-temperature-side heat-medium pumped by the low-temperature heat-medium pump 51 flows into the radiator 19. The low-temperature-side heat medium cooled by the radiator 19 flows into the cooling water passage 80a of the battery 80. As a result, the battery 80 to be cooled.

(9) Parallel dehumidification and waste heat recovery mode

The parallel dehumidification and waste heat recovery mode is an operation mode for cooling the battery 80 and dehumidifying and heating the vehicle cabin by reheating the cooled and dehumidified blown air and blowing the reheated blown air into the vehicle cabin. Specifically, the parallel dehumidification and exhaust heat recovery mode is an operation mode for reheating cooled blown air using heat received from the outside air and the battery 80 as a heat source.

The parallel dehumidification and waste heat recovery mode is executed when the air conditioner switch is turned on, the outside air temperature Tan is higher than the reference outside air temperature KTam, the target blowing temperature TAO is higher than the cooling reference temperature α1, and the target blowing temperature TAO is higher than the dehumidification reference temperature β1. Furthermore, the parallel dehumidification and waste heat recovery mode is executed when it is determined that the cooling of the battery 80 is required.

In the parallel dehumidification and waste heat recovery mode, the controller 60 opens the high-pressure open/close valve 15a and also opens the low-pressure open/close valve 15b. The controller 60 places the heating expansion valve 14a in a throttled state, places the cabin cooling expansion valve 14b in a throttled state, and places the device cooling expansion valve 14c in a throttled state. The control device 60 controls the operation of the integrated evaporation pressure adjustment valve 20 such that one of the first inlet port 201a and the second inlet port 201b is half open (in a throttled state) or fully open.

The controller 60 operates the high-temperature heat medium pump 41 to exert the predetermined pumping power. The control device 60 operates the low-temperature heat medium pump 51 to exert the predetermined pumping power.

Therefore, in the refrigeration cycle device 10, in the parallel dehumidification and waste heat recovery mode, the refrigerant circulates in the order of the compressor 11, the water-refrigerant heat exchanger 12, the first three-way junction 13a, the heating expansion valve 14a, the outdoor heat exchanger 16, the heating passage 22b, the integrated evaporating pressure adjusting valve 20, of the receiver 21 and the compressor 11. Further, the refrigerant circulates in the order of the compressor 11, the water-refrigerant heat exchanger 12, the first three-way junction 13a, the bypass passage 22a, the fourth three-way junction 13d, the cabin cooling expansion valve 14b, the indoor evaporator 18, the integrated evaporating pressure adjusting valve 20, the accumulator 21 and the compressor 11. Further, the refrigerant circulates in the order of the compressor 11, the water-refrigerant heat exchanger 12, the first three-way joint 13a, the bypass passage gs 22a, the fourth three-way junction 13d, the device cooling expansion valve 14c, the cooler 19, the integrated evaporation pressure adjusting valve 20, the accumulator 21 and the compressor.

That is, in the refrigeration cycle device 10 in the parallel dehumidification and waste heat recovery mode, one refrigerant branched at the first three-way junction 13a flows into the outdoor heat exchanger 16, and the other refrigerant flows into the fourth three-way junction 13d. Furthermore, one refrigerant branched at the fourth three-way joint 13d flows into the indoor evaporator 18, and the other refrigerant flows into the radiator 19.

The refrigerant cycle is switched to a refrigerant cycle in which the refrigerant flowing out from the outdoor heat exchanger 16, the refrigerant flowing out from the indoor evaporator 18, and the refrigerant flowing out from the radiator 19 are merged by the integrated evaporating pressure adjustment valve 20. That is, in the refrigeration cycle device 10 in the parallel dehumidification and waste heat recovery mode, the refrigerant cycle is switched to a refrigerant cycle in which the indoor evaporator 18, the radiator 19, and the outdoor heat exchanger 16 are connected in parallel to flow refrigerant.

In the refrigerant cycle described above, the control device 60 appropriately controls the operations of various control target devices. For example, the controller 60 controls the throttle opening of the device cooling expander 14c to a predetermined reference opening for a parallel dehumidification and waste heat recovery mode. The controller 60 controls the heating expansion valve 14a and the cabin expansion valve 14b in a manner similar to that in the parallel dehumidification mode.

The controller 60 controls the operation of the integrated evaporating pressure adjustment valve 20 such that the evaporator temperature Tefin approaches the target evaporator temperature TEO as in the parallel dehumidification mode.

Specifically, when the evaporator temperature Tefin is lower than the target evaporator temperature TEO, the controller 60 controls the operation of the integrated evaporation pressure adjustment valve 20 to fully open the first inlet port 201a and to half open the second inlet port 201b (to change the second inlet port 201b into a throttled to bring/put into condition). As a result, the refrigerant evaporating pressure in the outdoor heat exchanger 16 becomes/is lower than the refrigerant evaporating pressure in the indoor evaporator 18.

At this time, since the third inlet port 201c is fully open, the refrigerant evaporation pressure in the radiator 19 is the same as the refrigerant evaporation pressure in the outdoor heat exchanger 16.

When the compressor temperature Tefin is higher than the target evaporator temperature TEO, the controller 60 controls the operation of the integrated evaporating pressure adjustment valve 20 to half open the first inlet port 201a (to bring the first inlet port 201a to a throttled state) and to open the second inlet port 201b to open fully. As a result, the refrigerant evaporation pressure in the outdoor evaporator 16 is/becomes higher than the refrigerant evaporation pressure in the indoor evaporator 18.

At this time, since the third inlet port 201c is fully open, the refrigerant evaporating pressure in the radiator 19 is the same as the refrigerant evaporating pressure in the indoor evaporator 18. The other control target devices are controlled in a same manner as in the parallel dehumidifying mode.

Therefore, in the refrigeration cycle device 10, in the parallel dehumidification and waste heat recovery mode, a vapor evaporation cycle is formed in which the water-refrigerant heat exchanger 12 functions (operates, functions) as a condensing unit and the outdoor heat exchanger 16, indoor evaporator 18, and cooler 19 functions (operates, to serve).

As a result, in the refrigeration cycle device 10 in the parallel dehumidification and waste heat recovery mode, the high-temperature-side heat medium can be heated by the water-refrigerant heat exchanger 12 . The blown air can be cooled by the internal evaporator 18 . The low-temperature side heat medium can be cooled by the cooler 19 .

In the high temperature side heat medium circuit 40 in the parallel dehumidification and waste heat recovery mode, the high temperature side heat medium pumped by the high temperature heat medium pump 41 flows into the water-refrigerant heat exchanger 12. The high temperature side heat medium heated by the water-refrigerant heat exchanger 12 flows into the heater core 42

In the low-temperature-side heat-medium circuit 50 in the parallel dehumidification and waste-heat recovery mode, the low-temperature-side heat-medium pumped by the low-temperature heat-medium pump flows into the radiator 19. The low-temperature-side heat medium cooled by the radiator 19 flows into the cooling water passage 80a of the Battery 80. As a result, the battery 80 can be cooled. In other words, the low-temperature-side heat medium can absorb the waste heat from the battery 80 .

In the indoor air conditioning unit 30 in the parallel dehumidification and exhaust heat recovery mode, part of the blown air cooled and dehumidified by the indoor evaporator 18 is reheated by the heater core 42, and the blown air whose temperature has been regulated (regulated) to become the Approach target blowing temperature TAO, blown into the vehicle cabin. As a result, the vehicle cabin can be dehumidified and heated.

In the parallel dehumidification and waste heat recovery mode, the refrigerant pressure in the outdoor heat exchanger 16 can be regulated to be either higher or lower than the refrigerant evaporating pressure in the indoor evaporator 18 by the action of the integrated evaporating pressure adjustment valve 20 . As a result, the amount of heat absorbed from the outside air can be increased with the increase in the target blowing temperature TAO, and the ability to heat the blowing air in the heater core 42 can be regulated in a wide range, like in the parallel dehumidification mode.

In addition, in the parallel dehumidification and waste heat recovery mode, the refrigerant pressure in the radiator 19 can be regulated to be equal to a lower value of the refrigerant evaporation pressure in the outdoor heat exchanger 16 and the refrigerant evaporation pressure in the indoor evaporator 18 of the battery 80 can be increased with the increase in the target blowing temperature TAO, thereby improving the capability of heating the blowing air in the heater core 42 more than that in the parallel dehumidifying mode.

As described above, the refrigeration cycle device 10 according to the present embodiment can switch various operation modes. As a result, the vehicle air conditioner 1 can perform comfortable air conditioning in the vehicle cabin while appropriately controlling the temperature of the battery 80 .

In the refrigeration cycle device 10, two evaporating units may be connected in parallel with each other with respect to refrigerant flow in (2) cooling and battery cooling mode, (4) parallel dehumidifying mode, and (6) outdoor air heating and waste heat recovery mode. That is, when one of a plurality of evaporating units is defined as a first evaporating unit and another is defined as a second evaporating unit, the first evaporating unit and the second evaporating unit may be connected in parallel to the refrigerant flow.

The integrated evaporating pressure adjustment valve 20 can regulate the refrigerant evaporating pressure in the first evaporating unit to be either higher or lower than the refrigerant evaporating pressure in the second evaporating unit. Therefore, in the refrigeration cycle device 10, the refrigerant evaporating temperature in one of a plurality of evaporating units connected in parallel with each other with respect to the refrigerant flow direction can be appropriately regulated without affecting the refrigerant evaporating temperature in the other evaporating unit.

In the refrigeration cycle device 10, three evaporating units may be connected in parallel with each other with respect to the refrigerant flow in the (9) parallel dehumidification and waste heat recovery mode. That is, when an evaporating unit other than the first evaporating unit and the second evaporating unit among the plurality of evaporating units is defined as a third evaporating unit, the first evaporating unit, the second evaporating unit, and the third evaporating unit may be connected in parallel to the refrigerant flow be.

The integrated evaporating pressure adjustment valve 20 regulates the refrigerant evaporating pressure in the third evaporating unit to a value that is the same as a lower value of the refrigerant evaporating pressure in the first evaporating unit and the second evaporating unit. As a result, control for regulating (regulating) the refrigerant evaporating pressures in the plurality of evaporating units is not unnecessarily complicated.

This is effective when the evaporating units have at least the outdoor heat exchanger 16 that exchanges heat between the refrigerant and the outside air, the indoor evaporator 18 that exchanges heat between the refrigerant and the blown air, and the cooler 19 that exchanges heat between the refrigerant and the low-temperature-side heat medium exchanges, which is a cooling target, include.

Specifically, in order to cause the outdoor heat exchanger 16 to function (operate, act) as an evaporation unit, it is necessary that is, the refrigerant evaporating temperature is lower than the outside air temperature Tam. Therefore, the refrigerant evaporating pressure in the outdoor heat exchanger 16 is required to be regulated (controlled) depending on the outside air temperature Tam.

It is further required that the refrigerant evaporation pressure in the indoor evaporator 18 be regulated (controlled) in order to prevent icing of the indoor evaporator 18 for the purpose of performing comfortable air conditioning in the vehicle cabin. Therefore, for example, in the refrigeration cycle device 10 according to the present embodiment, the refrigerant evaporation temperature of the indoor evaporator 18 is regulated to 1°C or higher.

On the other hand, the refrigerant evaporating temperature in the radiator 19 can be regulated in a range wider than that of the refrigerant evaporating temperature in the outdoor heat exchanger 16 or the indoor evaporator 18, although the self-heating amount of the battery 80 is required to be considered. When the radiator 19 is the third evaporating unit, control for regulating (regulating) the refrigerant evaporating pressures in the plurality of evaporating units is not unnecessarily complicated.

In the refrigeration cycle device 10, the device cooling expansion valve 14c functions as a blocking unit that blocks the flow of the refrigerant into the third evaporation unit when the refrigerant evaporates in the first evaporation unit and the second evaporation unit. Therefore, when the refrigerant evaporation temperature in the radiator 19 is unnecessarily lowered and the temperature of the low-temperature side heating medium can be extremely lowered, the flow of the refrigerant into the radiator 19 may be blocked.

In other words, the refrigeration cycle device 10 according to the present embodiment includes the device cooling expansion valve 14c that functions (operates, acts) as a blocking unit. Therefore, in the (9) parallel dehumidification and waste heat recovery mode, when there is a risk that the temperature of the low-temperature-side heating medium is extremely reduced, the device cooling expansion valve 14c can be brought into a fully closed state and the mode can be switched to the (4) parallel dehumidification mode will.

The integrated evaporation pressure adjustment valve 20 has the single valve body 202 and the single drive unit 203 that regulate (regulate) the passage cross-sectional areas of a plurality of refrigerant passages simultaneously. With this configuration, the refrigerant evaporating temperatures in the plurality of evaporating units connected in parallel to each other can be appropriately regulated (regulated) without complicating or enlarging the cycle configuration compared to a case where individual evaporating pressure adjusting valves are installed on the downstream side of the plurality of Evaporation units are arranged in a refrigerant flow.

Furthermore, the integrated evaporation pressure adjustment valve 20 has a backflow prevention function, and thus at the time of switching the operation mode or the like, it is possible to prevent the refrigerant from flowing from the suction port side of the compressor 11 to the evaporation unit side.

(Second embodiment)

The present embodiment will describe below an example in which an integrated evaporation pressure adjustment valve 210 shown in 6 until 10 is shown, is used instead of the integrated evaporation pressure adjustment valve 20.

The integrated evaporation pressure adjustment valve 210 has a body 211 , a valve body 212 and a drive unit 213 . The body 211 is a bottomed cylindrical member made of metal. The body 211 forms an outer shell of the integrated evaporation pressure adjustment valve 210 and further forms a columnar inner space therein.

Three inlet ports, that is, a first inlet port 211 a , a second inlet port 211 b , and a third inlet port 211 c , through which the refrigerant flows into the interior, are formed on the cylinder side surface of the body 211 . As in 6 1, the three inlet ports are sequentially formed in the central axis direction of the body 211. As shown in FIG. The first inlet port 211a, the second inlet port 211b and the third inlet port 211c correspond to the first inlet port 201a, the second inlet port 201b and the third inlet port 201c of the integrated evaporation pressure adjusting valve 20 described in the first embodiment.

As in 6 1, the driving unit 213 is arranged on one end side of the body 211 in the central axis direction. As in 6 and 7 shown is a discharge port 211d through which refrigerant is discharged from an interior space flows is formed on the other end side of the body 211 in the central axis direction.

The drive unit 203 is an electric actuator that moves the valve body 212 arranged in the interior of the body 211 around the central axis. The basic configuration of the drive unit 213 is the same as that of the drive unit 203 in the integrated evaporation pressure adjustment valve 20 described in the first embodiment.

The valve body 212 is a cylindrical member made of metal. As in 8th and 9 As shown, the valve body 212 is accommodated in the interior space of the body 211 . The center axis of the valve body 212 is arranged coaxially with the center axis of the interior of the body 211 . The outer diameter of the valve body 212 is slightly smaller than the inner diameter of the columnar interior of the body 211.

For this reason, as in 8th 1, a sealing member 205 that prevents the refrigerant from leaking from the gap between the valve body 212 and the body 211 is disposed on the inner peripheral side surface of the body 211. As shown in FIG. When the driving unit 213 moves the valve body 212 about the central axis, the outer peripheral side surface of the valve body 212 slides on the sealing member 215.

As in 9 and 10 1, a first communication hole 212a, a second communication hole 212b, and a third communication hole 212c communicating the outer peripheral side with the inner peripheral side of the valve body 212 are formed in the side surface of the valve body 212. The first connection hole 212a, the second connection hole 212b, and the third connection hole 212c are formed in a band shape extending in a circumferential direction (ie, a rotating direction).

The first connection hole 212a, the second connection hole 212b, and the third connection hole 212c are arranged in series in the central axis direction. The first communication hole 212a, the second communication hole 212b, and the third communication hole 212c are arranged to overlap the first inlet port 211a, the second inlet port 211b, and the third inlet port 211c, respectively.

As in the unwound view of 10 1, the width dimension (that is, the axial dimension) of each hole is different from the first communication hole 212a, the second communication hole 212b, and the third communication hole 212c formed in the band shape. As a result, when the drive unit 213 moves the valve body 212 about the central axis, the openings of the first inlet port 211a, the second inlet port 211b and the third inlet port 211c can vary depending on the width dimensions of the first communication hole 212a, the second communication hole 212b and the third communication hole 212c be changed.

In particular, the inlet port overlapping the wide portion of each communication hole is fully open. The inlet port overlapping with the narrow portion of the connection hole is half open. The half-open inlet port functions (works, acts) as a throttle passage to perform a refrigerant pressure decompression action. The inlet port, which overlaps with the portion without a connection hole, is completely closed.

As in 10 1, in the valve body 212 of the present embodiment, the patterns of the width dimensions of the first communication hole 212a, the second communication hole 212b, and the third communication hole 212c are changed. According to the pattern of the present embodiment, when the drive unit 213 displaces the valve body 212, any one of the first inlet port 211a, the second inlet port 211b, and the third inlet port 211c can be a throttle passage or fully closed. Then the remaining two ports can be fully opened.

The valve body 212 is a single opening regulation unit that regulates passage cross-sectional areas (specifically, opening areas of the first inlet port 211a, the second inlet port 211b, and the third inlet port 211c) of refrigerant passages in which the refrigerants flowing out from the evaporating units flow, respectively. It should be noted that 10 14 is an explanatory diagram for explaining the shape of each communication hole and the opening of each intake port using the developed view of the valve body 212. FIG.

Each of the first inlet port 211a to the third inlet port 211c has a reed valve (not shown) that prevents the refrigerant from flowing from the interior side of the body 211 to the plurality of evaporation units side. That is, the integrated evaporation pressure adjustment valve 210 has a reverse flow prevention function of preventing the refrigerant from flowing from the outlet port 211d side to the plurality of evaporation units side.

Other configurations of the refrigeration cycle devices 10 and the vehicle air conditioner 1 are the same as those in the first embodiment. The vehicle air conditioner 1 of the present embodiment can have eight operation modes corresponding to (1) cooling mode, (2) cooling and battery cooling mode, (3) serial dehumidifying mode, (4) parallel dehumidifying mode, (5) outside air heating mode, (6) the outdoor air heating and exhaust heat recovery mode, the (7) exhaust heat recovery and heating mode, and the (8) battery cooling mode described in the first embodiment.

Thus, the refrigeration cycle device 10 integrated with the evaporation pressure adjustment valve 210 according to the present embodiment can achieve the same effects as those of the first embodiment.

That is, the refrigerant evaporating temperature in one of a plurality of evaporating units connected in parallel with each other with respect to refrigerant flow can be appropriately regulated (regulated) without affecting the refrigerant evaporating temperature in another evaporating unit. In addition, the refrigerant evaporating temperatures in the plurality of evaporating units connected in parallel to each other can be appropriately regulated (controlled) without complicating or increasing a cycle configuration.

As in 10 1, in the integrated evaporation pressure adjustment valve 210 of the present embodiment, the patterns of the width dimensions of the first communication hole 212a, the second communication hole 212b, and the third communication hole 212c are changed. For this reason, all ports of the first inlet port 211a, the second inlet port 211b and the third inlet port 211c cannot be fully opened, but the width dimension patterns are not limited to this.

That is, it is possible to form a width dimension pattern that can fully open all ports of the first inlet port 211a, the second inlet port 211b, and the third inlet port 211c. In this case, the operation can be performed in the (9) parallel dehumidification and waste heat recovery mode.

(Third embodiment)

The present embodiment describes a refrigeration cycle device 10a applied to a vehicle air conditioner 1a shown in the overall configuration diagram of FIG 11 is shown.

In 11 For ease of illustration, the indoor air conditioning unit 30, the high-temperature-side heat-medium circuit 40, and the low-temperature-side heat-medium circuit 50 are omitted. Accordingly, in the refrigeration cycle device 10a as well, the water passage of the water-refrigerant heat exchanger 12 is connected to the high-temperature-side heat medium circuit 40 . The water passage of the radiator 19 is connected to the low temperature side heat medium circuit 50 . The indoor evaporator 18 is arranged in the case 31 of the indoor air conditioning unit 30 .

In the refrigeration cycle device 10a, the accumulator 21 is omitted and a receiver 23 is used. The receiver 23 is a high-pressure-side gas-liquid separator that separates (separates) high-pressure refrigerant flowing out from a heat exchanger that functions (works, acts) as a condenser into gas and liquid. Furthermore, the receiver 23 causes part of the separated liquid-phase refrigerant to flow to the downstream side and stores the remaining liquid-phase refrigerant as a surplus refrigerant in the cycle.

The inlet port side of the heating expansion valve 14a is connected to an outlet port of the third three-way joint 13a in the refrigeration cycle device 10a via a first high-pressure open/close valve 15c and a fifth three-way joint 13e. The inlet port side of the scavenger 23 is connected to the other outlet port of the first three-way joint 13a via an inlet port side passage 22c. A second high-pressure open/close valve 15d and the second three-way joint 13b are arranged in the intake port-side passage 22c.

The first high-pressure open/close valve 15c is an electromagnetic valve that opens and closes a refrigerant passage connecting an outlet port of the first three-way joint 13a and an inlet port of the fifth three-way joint 13e. The outlet port side of the scavenger 23 is connected to the other outlet port side of the fifth three-way junction 13e via an outlet port side passage 22d. A sixth three-way joint 13f and a second check valve 17b are arranged in the outlet-port-side passage 22d. The inlet port side of the fourth three-way connector connection point is connected to the outlet port of the sixth three-way connection point 13f.

The second check valve 13b allows the refrigerant to flow from the sixth three-way junction 13f side to the fifth way junction 13e side, and prevents the refrigerant from the fifth three-way junction 13e side to the sixth three-way junction 13e side 13f flows. In other words, the second check valve 17b allows the refrigerant to flow from the outlet port side of the receiver 23 to the inlet port side of the heating expansion valve 14a and prevents the refrigerant from flowing from the inlet port side of the heating expansion valve 14a to the outlet port side of the receiver 23.

The basic configurations of the fifth three-way junction 13e and the sixth three-way junction 13f are the same as those of the first three-way junction 13a and the like. The basic configurations of the first high pressure opening/closing valve 15c and the second high pressure opening/closing valve 15d are the same as those of the high pressure opening/closing valve 15a and the like described in the first embodiment. The first high pressure opening/closing valve 15c and the second high pressure opening/closing valve 15d are refrigerant cycle switching units. The basic configuration of the second check valve 17b is the same as that of the check valve 17 described in the first embodiment. Note that for convenience of description, the check valve 17 described in the first embodiment is referred to as a “first check valve 17a” in the present embodiment.

In the refrigeration cycle device 10 a , the suction port side of the compressor 11 is connected to the discharge port 201 d of the integrated evaporation pressure adjustment valve 20 . Accordingly, the compressor 11 sucks the refrigerant flowing out from the integrated evaporation pressure adjustment valve 20 .

Other configurations of the refrigeration cycle device 10a and the vehicle air conditioner 1a are the same as those of the refrigeration cycle device 10 and the vehicle air conditioner 1 described in the first embodiment. In addition, the vehicle air conditioner 1a according to the present embodiment can have seven operation modes corresponding to (1) cooling mode, (2) cooling and battery cooling mode, (4) parallel dehumidification mode, (5) outside air heating mode, (6) outside air heating and waste heat recovery mode, the (8) battery cooling mode and the (9) parallel dehumidification and waste heat recovery mode described in the first embodiment. The detailed operation of each operation mode is described below.

(1) Cooling mode

In the cooling mode, the controller 60 opens the first high-pressure opening/closing valve 15c, closes the second high-pressure opening/closing valve 15d, and also closes the low-pressure opening/closing valve 15b. The controller 60 places the heating expansion valve 14a in a fully open state, places the cabin cooling expansion valve 14b in a throttled state, and places the device cooling expansion valve 14c in a fully closed state.

Therefore, in the refrigeration cycle device 10a, in the cooling mode, the refrigerant cycle is switched to a refrigerant cycle in which the refrigerant is discharged in the order of the compressor 11, the water-refrigerant heat exchanger 12, the heating expander 14a which is fully open, the outdoor heat exchanger 16, the first check valve 17a , the receiver 23, the cabin cooling expansion valve 14b, the indoor evaporator 18, the integrated evaporating pressure adjusting valve 20 and the compressor 11 circulates.

In the refrigerant cycle described above, the control device 60 appropriately controls operations of various control target devices. For example, the controller 60 controls the throttle opening of the cabin cooling expansion valve 14b such that the superheat degree SHE of the refrigerant at the outlet port side of the indoor evaporator 18 approaches the predetermined target superheat degree SHEO.

The other control target devices are controlled in a similar manner as in the cooling mode of the first embodiment. Therefore, the vehicle cabin can be cooled as in the first embodiment.

In the refrigeration cycle device 10a in the cooling mode, the excess refrigerant in the cycle is stored in the receiver 23, and thus the refrigerant at the outlet port side of the indoor evaporator 18 can have the superheat degree. As a result, the amount of heat absorbed by the refrigerant in the indoor evaporator 18 can be increased compared to the cycle in which the excessive refrigerant in the cycle is collected ler is stored, and thus the ability to cool the blown air can be improved.

(2) Cooling and battery cooling mode

In the cooling and battery cooling mode, the controller 60 opens the first high-pressure open/close valve 15c, closes the second high-pressure open/close valve 15d, and also closes the low-pressure open/close valve 15b. The controller 60 places the heating expansion valve 14a in a fully open state, places the cabin cooling expansion valve 14b in a throttled state, and places the device cooling expansion valve 14c in a throttled state.

Therefore, the refrigerant circulates in the refrigeration cycle device 10a in the cooling and battery cooling mode in the order of the compressor 11, the water-refrigerant heat exchanger 12, the full-open heating expansion valve 14a, the outdoor heat exchanger 16, the first check valve 17a, the receiver 23, the fourth three-way junction 13d , the cabin cooling expansion valve 14b, the indoor evaporator 18, the integrated evaporation pressure adjusting valve 20 and the compressor 11. Further, the refrigerant circulates in the order of the compressor 11, the water-refrigerant heat exchanger 12, the full-open heating expansion valve 14a, the outdoor heat exchanger 16, the first check valve 17a , the receiver 23, the fourth three-way junction 13d, the device refrigeration expansion valve 14c, the cooler 19, the integrated evaporating pressure adjusting valve 20 and the compressor 11.

That is, in the refrigeration cycle device 10a, in the cooling and battery cooling mode, the refrigerant cycle is switched to a refrigerant cycle in which the indoor evaporator 18 and the radiator 19 are connected in parallel to flow refrigerant.

In the refrigerant cycle described above, the control device 60 appropriately controls the operations of various control target devices. For example, the control device 60 for the cabin cooling expansion valve 14b and the device cooling expansion valve 14c regulates the opening ratio of the throttle opening of the device cooling expansion valve 14c to the throttle opening of the cabin cooling expansion valve 14b such that the superheat degree SHE of the refrigerant at the outlet port side of the indoor evaporator 18 and the superheat degree SHC at the outlet port side of the radiator 19 approach the target superheat degree SHEO, which is equivalent to the superheat degree SHC.

The other control target devices are controlled in a similar manner as in the cooling and battery cooling mode of the first embodiment. Therefore, the vehicle cabin and the battery 80 are cooled as in the first embodiment. At this time, the temperature of the low-temperature side heating medium can be regulated in a wide temperature range depending on the heat generation amount of the battery 80 or the like by the action of the integrated evaporation pressure adjustment valve 20 .

In the refrigeration cycle device 10a in the cooling and battery cooling mode, the refrigerant on the outlet port side of the indoor evaporator 18 and the refrigerant on the outlet port side of the radiator 19 may have the superheat degree. As a result, the amount of heat absorbed by the refrigerant in the indoor evaporator 18 can be increased, and hence the ability to cool the blown air can be improved. Furthermore, the amount of heat that the refrigerant in the radiator 19 absorbs can be increased, whereby the ability to cool the battery 80 can be improved.

(4) Parallel dehumidification mode

In the parallel dehumidifying mode, the controller 60 closes the first high-pressure open/close valve 15c, opens the second high-pressure open/close valve 15d, and also opens the low-pressure open/close valve 15b. The controller 60 places the heating expansion valve 14a in a throttled state, places the cabin cooling expansion valve 14b in a throttled state, and places the device cooling expansion valve 14c in a fully closed state.

Therefore, the refrigerant in the refrigeration cycle device 10a circulates in the parallel dehumidifying mode in the order of the compressor 11, the water-refrigerant heat exchanger 12, the inlet-port-side passage 22c, the receiver 23, the sixth three-way joint 13f in the outlet-port-side passage 22d, the heating expansion valve 14a, the outdoor heat exchanger 16, the heating passage 22b, the integrated evaporation pressure adjusting valve 20 and the compressor 11. Further, the refrigerant circulates in the order of the compressor 11, the water-refrigerant heat exchanger 12, the inlet port side passage 22c, the receiver 23, the sixth three-way junction 13f in the outlet port side passage 22d, the cabin cooling expansion valve 14b, the indoor evaporator 18, the integrated evaporation pressure adjustment valve 20 and the compressor 11.

In the refrigerant cycle described above, the control device 60 appropriately controls the operations of various control target devices. For example, for the heating expansion valve 14a and the cabin cooling expansion valve 14b, the controller 60 controls the opening ratio of the throttle opening of the cabin cooling expansion valve 14b to the throttle opening of the heating expansion valve 14a so that the superheat degree SHE of the refrigerant at the outlet port side of the indoor evaporator 18 approaches the target superheat degree SHEO, which is the superheat degree SHE corresponds.

The other control devices are controlled in a manner similar to that in the parallel dehumidifying mode of the first embodiment. Therefore, the vehicle cabin is dehumidified and heated as in the first embodiment. At this time, the ability to heat the blown air in the heater core 42 can be controlled in a wide range depending on which target blowing temperature TAO is reached by the action of the integrated evaporating pressure adjustment valve 20 .

In the refrigeration cycle device 10a in the parallel dehumidifying mode, the refrigerant on the outlet port side of the outdoor heat exchanger 16 and the refrigerant on the outlet port side of the indoor evaporator 18 may have the superheat degree. As a result, the amount of heat absorbed by the refrigerant in the outdoor heat exchanger 16 can be increased, and thus the ability to heat the blown air can be improved. Furthermore, the amount of heat absorbed by the refrigerant in the indoor evaporator 18 can be increased, and hence the ability to cool the blown air can be improved.

(5) Outdoor air heating mode

In the outside-air heating mode, the controller 60 closes the first high-pressure opening/closing valve 15c, opens the second high-pressure opening/closing valve 15d, and also opens the low-pressure opening/closing valve 15b. The controller 60 places the heating expansion valve 14a in a throttled state, places the cabin cooling expansion valve 14b in a fully closed state, and places the device cooling expansion valve 14c in a fully closed state.

Therefore, in the refrigeration cycle device 10a, in the outdoor air heating mode, the refrigerant cycle is switched to a refrigerant cycle in which the refrigerant is heated in the order of the compressor 11, the water-refrigerant heat exchanger 12, the inlet port side passage 22c, the receiver 23, the outlet port side passage 22d, the heating expansion valve 14a , the outdoor heat exchanger 16, the heating passage 22b, the integrated evaporating pressure adjustment valve 20 and the compressor 11 circulates.

In the refrigerant cycle described above, the control device 60 suitably controls the operation of various control target devices. For example, the controller 60 controls the throttle opening of the heating expansion valve 14a so that the superheat degree SHA of the refrigerant at the outlet port side of the outdoor heat exchanger 16 approaches a predetermined target superheat degree SHAO. The degree of superheat SHA is determined by using the second temperature T2 and the second pressure P2.

The other control devices are controlled in a manner similar to that in the outside air heating mode of the first embodiment. Therefore, the vehicle cabin is heated as in the first embodiment.

In the refrigeration cycle device 10a in the outdoor air heating mode, the refrigerant at the outlet port side of the outdoor heat exchanger 16 may have the superheat degree. As a result, the amount of heat absorbed by the refrigerant in the outdoor heat exchanger 16 can be increased, and thus the ability to heat the blown air can be improved.

(6) Outdoor air heating and waste heat recovery mode

In the outside air heating and waste heat recovery mode, the controller 60 closes the first high pressure opening/closing valve 15c, opens the second high pressure opening/closing valve 15d, and also opens the low pressure opening/closing valve 15b. The controller 60 places the heating expansion valve 14a in a throttled state, places the cabin cooling expansion valve 14b in a fully closed state, and places the device cooling expansion valve 14c in a throttled state.

Therefore, in the refrigeration cycle device 10a, the refrigerant circulates in the order of the compressor 11, the water-refrigerant heat exchanger 12, the inlet-port-side passage 22c, the receiver 23, the sixth three-way junction 13f in the outlet-port-side passage 22d, the heating expansion valve 14a, of the outdoor heat exchanger 16, the heating passage 22b, the integrated evaporating pressure adjustment valve 20 and the condenser ters 11. Further, the refrigerant circulates in the order of the compressor 11, the water-refrigerant heat exchanger 12, the inlet-port-side passage 22c, the receiver 23, the sixth three-way junction 13f in the outlet-port-side passage 22d, the integrated evaporation pressure adjusting valve 20, and the compressor 11.

In the refrigerant cycle described above, the control device 60 appropriately controls the operations of various control target devices. For example, for the heating expansion valve 14a and the device cooling expansion valve 14c, the control device 60 regulates the opening ratio of the throttle opening of the cooling expansion valve 14c to the throttle opening of the heating expansion valve 14a so that the superheat degree SHC of the refrigerant at the outlet port side of the radiator 19 approaches a target superheat degree SHCO, which is the superheat degree SHC corresponds.

The other control devices are controlled in a manner similar to that in the outdoor air heating and waste heat recovery mode of the first embodiment. Therefore, the vehicle cabin can be heated and the battery 80 can be cooled as in the first embodiment. At this time, the ability to heat the blown air in the heater core 42 can be regulated in a wide range depending on what ability to heat the blown air is required while the battery 80 is appropriately cooled by the action of the integrated evaporation pressure adjustment valve 20.

In the refrigeration cycle device 10a in the parallel dehumidifying mode, the refrigerant on the outlet port side of the outdoor heat exchanger 16 and the refrigerant on the outlet port side of the indoor evaporator 18 may have the superheat degree. As a result, the amount of heat absorbed by the refrigerant in the outdoor heat exchanger 16 can be increased, and hence the ability to heat the blown air can be improved. Furthermore, the amount of heat absorbed by the refrigerant in the radiator 19 can be increased, and hence the ability to cool the battery 80 can be improved.

(8) battery cooling mode

In the battery cooling mode, the controller 60 opens the first high-pressure open/close valve 15c, closes the second high-pressure open/close valve 15d, and also closes the low-pressure open/close valve 15b. The controller 60 places the heating expansion valve 14a in a fully open state, places the cabin cooling expansion valve 14b in a fully closed state, and places the device cooling expansion valve 14c in a throttled state.

Therefore, in the refrigeration cycle device 10a in the battery cooling mode, the refrigerant circulates in the order of the compressor 11, (the water-refrigerant heat exchanger 12), the full-open heating expansion valve 14a, the outdoor heat exchanger 16, the receiver 23, the device cooling expansion valve 14c, the radiator 19, the integrated evaporation pressure adjustment valve 20 and the compressor 11.

In the refrigerant cycle described above, the control device 60 appropriately controls the operations of various control target devices. For example, the throttle opening of the device cooling expansion valve 14c is controlled so that the superheat degree SHC of the refrigerant at the outlet port side of the radiator 19 approaches the target superheat degree SHCO.

The other control devices are controlled in a manner similar to that in the battery cooling mode of the first embodiment. Therefore, the battery 80 can be cooled as in the first embodiment.

In the refrigeration cycle device 10a in the battery cooling mode, the refrigerant at the outlet port side of the radiator 19 may have the superheat degree. As a result, the amount of heat absorbed by the refrigerant in the radiator 19 can be increased, and hence the ability to cool the battery 80 can be improved.

(9) Parallel dehumidification and waste heat recovery mode

In the parallel dehumidification mode and waste heat recovery mode, the controller 60 closes the first high-pressure open/close valve 15c, opens the second high-pressure open/close valve 15d, and opens the low-pressure open/close valve 15b. The controller 60 places the heating expansion valve 14a in a throttled state, places the cabin cooling expansion valve 14b in a throttled state, and places the device cooling expansion valve 14c in a throttled state.

Therefore, in the parallel dehumidification and waste heat recovery mode, the refrigerant in the refrigeration cycle device 10a circulates in the order of the compressor 11, the water-refrigerant heat exchanger 12, the inlet port side passage 22c, the receiver 23, the sixth three-way junction 13f in the outlet port side passage 22d, the heating expansion valve 14a, the outdoor heat exchanger 16, the heating passage 22b, the integrated evaporation pressure adjustment valve 20 and the compressor 11. Further, the refrigerant circulates in the order of the compressor 11, the water-refrigerant heat exchanger 12, the inlet port side passage 22c, the receiver 23, the sixth three-way junction 13f in the outlet port-side passage 22d, the fourth three-way junction 13d, the cabin cooling expansion valve 14b, the indoor evaporator 18, the integrated evaporation pressure adjusting valve 20 and the compressor 11. Further, the refrigerant circulates in the order of the compressor 11, Heat exchanger 12 (water-refrigerant), inlet-port-side passage 22c, receiver 23, sixth three-way junction 13f in the outlet-port-side passage 22d, fourth three-way junction 13d, jig cooling expansion valve 14c, cooler 19, integrated evaporation pressure adjustment valve 20 and compressor 11.

In the refrigerant cycle described above, the control device 60 suitably controls the operation of various control target devices. For example, the controller 60 controls the throttle opening of the device cooling expansion valve 14c to a predetermined reference opening. The controller 60 controls the heating expansion valve 14a, the cabin cooling expansion valve 14b, and the integrated evaporating pressure adjustment valve 20 in a manner similar to that in the parallel dehumidification mode.

The other control devices are controlled in a manner similar to that in the parallel dehumidification and exhaust heat recovery mode of the first embodiment. Therefore, as in the first embodiment, the vehicle cabin can be dehumidified and heated, and the battery 80 can be cooled. At this time, the ability to heat the blown air in the heater core 42 can be controlled in a wide range depending on which target blowing temperature TAO is reached by the action of the integrated evaporating pressure adjustment valve 20 .

In the refrigeration cycle device 10a in the parallel dehumidification and waste heat recovery mode, the refrigerant at the outlet port side of the outdoor heat exchanger 16, the refrigerant at the outlet port side of the indoor evaporator 18, and the refrigerant at the outlet port side of the radiator 19 may have the superheat degree.

As a result, the amount of heat absorbed by the refrigerant in the outdoor heat exchanger 16 can be increased, and hence the ability to heat blown air can be improved. The amount of heat that the refrigerant in the indoor evaporator 18 absorbs can be increased, so the ability to cool blown air can be increased. Furthermore, the amount of heat absorbed by the refrigerant in the radiator 19 can be increased, and hence the ability to cool the battery 80 can be improved.

As described above, the refrigeration cycle device 10a according to the present embodiment can switch various operation modes. As a result, the vehicle air conditioner 1 can perform comfortable air conditioning of the vehicle cabin while appropriately regulating the temperature of the battery 80 . The refrigeration cycle device 10a according to the present embodiment can also obtain effects similar to the first embodiment.

That is, the refrigerant evaporating temperature in one of a plurality of evaporating units connected in parallel with respect to a refrigerant flow can be appropriately controlled without being affected by the refrigerant evaporating temperature in another evaporating unit. Furthermore, the refrigerant evaporating temperatures in the plurality of evaporating units connected in parallel with each other can be appropriately controlled without complicating or increasing a circuit configuration.

In the refrigeration cycle device 10a according to the present embodiment as described above, the refrigerant at the outlet port side of the heat exchanger working as an evaporator can have a degree of superheat, so that the amount of heat absorbed by the refrigerant in the heat exchanger working as an evaporator can be increased. As a result, the coefficient of performance of the cycle can be improved, and thus the ability to heat blown air, the ability to cool blown air, and the ability to cool the battery 80 can be improved.

(Fourth embodiment)

The present embodiment describes a refrigeration cycle device 10b applied to a vehicle air conditioner 1b as shown in the overall configuration diagram of FIG 12 is shown. In the refrigeration cycle device 10b, the outdoor heat exchanger 16, the high-temperature-side heat medium cycle, is omitted 40 and the low temperature side heat medium circuit 50, and a heat medium circuit 90 is used. In the refrigeration cycle device 10 b , the water-refrigerant heat exchanger 12 and the radiator 19 are connected to the heat medium circuit 90 .

The inlet port side of the receiver 23 is connected to the outlet port of a refrigerant passage in the refrigeration cycle device 10b. The inlet port side of the fourth three-way joint 13 d is connected to the outlet port side of the pickup 23 . Since the outdoor heat exchanger 16 is omitted in the refrigeration cycle device 10b, the first inlet port 201a of the integrated evaporation pressure adjustment valve 20 is closed.

As described in the first embodiment, a diaphragm valve (not shown) is arranged at each inlet port of the integrated evaporation pressure adjustment valve 20 . For this reason, in the integrated evaporation pressure adjustment valve 20, when nothing is connected to the first inlet port 201a, the first inlet port 201a can be closed. Needless to say, a plug or the like is attached to the first intake port 201a to close the first intake port.

Next, the heat medium circuit 90 is a heat medium circulation circuit that circulates a heat medium. As the heat medium, a fluid similar to the high-temperature-side heat medium or the low-temperature-side heat medium described in the first embodiment can be used.

In the heat medium circuit 90, the water passage of the water-refrigerant heat exchanger 12, the high-temperature heat-medium pump 41, the heater core 42, the water passage of the radiator 19, the low-temperature heat-medium pump 51, the cooling water passage 80a of the battery 80, a first three-way valve 91a, a second three-way valve 91b, a radiator 92, a first heat-medium three-way junction 93a to a fourth heat-medium three-way junction 93d, and the like are arranged. The basic configurations of the first heat-medium three-way joint 93a to the fourth heat-medium three-way joint 93d are similar to those of the first heat-medium three-way joint 13a.

In the heat medium circuit 90, the high-temperature heat medium pump 41 sucks the heat medium flowing from the water passage of the water-refrigerant heat exchanger 12 and pumps the heat medium to the inlet side of the first three-way valve 91a. The first three-way valve 91a is a three-way switching valve that switches between a flow path that lets the heat medium pumped by the high-temperature heat medium pump 41 flow to the heater core 42 side and a flow path that lets the heat medium flow to the radiator 92 side. The operation of the first three-way valve 91a is controlled by a control voltage output from the control device 60 .

The heat medium inlet port side of the heater core 42 is connected to an outlet port of the first three-way valve 91a. The one inlet port side of the first heat medium three-way joint 93a is connected to the other outlet port of the first three-way valve 91a.

In the heat medium circuit 90, the low-temperature heat medium pump 51 sucks the heat medium flowing from the water passage of the radiator 19 and pumps the heat medium to the inlet port side of the second three-way valve 91b. The second three-way valve 91 b is a three-way switching valve that switches between a flow path that lets the heat medium pumped by the low-temperature heat medium pump 51 flow to the heater core 42 side and a flow path that lets the heat medium flow to the radiator 92 side. The basic configuration of the second three-way valve 91b is similar to that of the first three-way valve 91a.

The inlet port side of the cooling water passage 80a in the battery 80 is connected to an outlet port of the second three-way valve 91b. The other inlet port side of the first heat medium three-way joint 93a is connected to the other outlet port of the second three-way valve 91b. The refrigerant inlet port side of the radiator 92 is connected to the outlet port of the first heat medium three-way joint 93a.

The radiator 92 is a heat exchanger that exchanges heat between the heating medium and the outside air blown by a fan (not shown). Similar to the outdoor heat exchanger 16 described in the first embodiment, the radiator 92 is arranged on the front side of the drive unit chamber. The inlet port side of the second heat medium three-way joint 93 b is connected to the refrigerant outlet port of the radiator 92 .

An inlet port side of the third heat medium three-way joint 93c is connected to connected to an outlet port side of the second heat medium three-way joint 93b. The heat medium outlet port side of the heater core 42 is connected to the other inlet port of the third heat medium three-way joint 93c. The inlet port side of the water passage in the water-refrigerant heat exchanger 12 is connected to the outlet port of the third heat medium three-way joint 93c.

The one inlet port side of the fourth heat-medium three-way joint 93d is connected to the other outlet port side of the second heat-medium three-way joint 93b. The outlet port side of the passage 80a of the cooling water in the battery 80 is connected to the other inlet side of the fourth heat medium three-way joint 93d. The inlet port side of the water passage in the radiator 19 is connected to the outlet port side of the fourth heat medium three-way joint 93d.

When the first three-way valve 91 a flows the heat medium to the heater core 42 side under the operation of the high-temperature heat medium pump 41 , the heat medium can circulate between the water-refrigerant heat exchanger 12 and the heater core 42 . As a result, the heating medium and the blown air can exchange heat in the heater core 42 . That is, the blown air can be heated by releasing heat of the heating medium to the blown air in the heater core 42 .

On the other hand, when the first three-way valve 91a flows the heat medium to the radiator 92 side in the operation of the high-temperature heat-medium pump 41 , the heat medium can circulate between the water-refrigerant heat exchanger 12 and the radiator 92 . As a result, the heat medium and the outside air can exchange heat in the radiator 92 . More specifically, the heat of the heat medium in the radiator 92 can be released to the outside air.

When the second three-way valve 91b flows the heat medium to the cooling water passage 80a side in the battery 80 in the operation of the low-temperature heat medium pump 51 , the heat medium can be circulated between the radiator 19 and the cooling water passage 80a of the battery 80 . The heat medium and the battery 80 can exchange heat in the cooling water passage 80a of the battery 80 . More specifically, the battery can be cooled by the heat medium cooled by the radiator 19 .

On the other hand, the heat medium can circulate between the radiator 19 and the radiator 92 when the second three-way valve 91b flows the heat medium to the radiator 92 side in the operation of the low-temperature heat medium pump 51 . As a result, the heat medium and outside air in the radiator 92 can exchange heat. More specifically, the heat medium cooled by the radiator 19 can absorb the heat of the outside air in the radiator 92 .

The control device 60 of the present embodiment does not control the operation of the first three-way valve 91a and the second three-way valve 91b so that the heat medium discharged from the high-temperature heat-medium pump 41 and the heat medium discharged from the low-temperature heat-medium pump 51 flow into the radiator 92 at the same time.

Other configurations of the refrigeration cycle device 10b and the vehicle air conditioner 1b are the same as those of the refrigeration cycle device 10 and the vehicle air conditioner 1 described in the first embodiment. The vehicle air conditioner 1b of the present embodiment can perform seven operation modes corresponding to (1) cooling mode, (2) cooling and battery cooling mode, (3) serial dehumidifying mode, (4) parallel dehumidifying mode, (5) outdoor air heating mode, (7 ) waste heat recovery and heating mode and (8) battery cooling mode. The detailed operation of each operation mode is described below.

(1) Cooling mode

In the cooling mode, the controller 60 places the cabin cooling expansion valve 14b in a throttled state and the device cooling expansion valve 14c in a fully closed state. The control device 60 controls the high-temperature heat-medium pump 41 to have the predetermined pumping capacity. The control device 60 controls the operation of the first three-way valve 91 a so that the medium discharged from the high-temperature heat medium pump 41 flows into the radiator 92 .

Therefore, in the refrigeration cycle device 10b, in the cooling mode, the refrigerant cycle is switched to a refrigerant cycle in which the refrigerant is mixed in the order of the compressor 11, the water-refrigerant heat exchanger 12, the receiver 23, the cabin cooling expansion valve 14b, the indoor evaporator 18, the integrated evaporation pressure adjusting valve 20, and of the compressor 11 circulates. In the heat medium circuit 90, in In the cooling mode, the cycle is switched to a cycle in which the heat medium circulates in the order of high-temperature heat-medium pump 41 , radiator 92 , water passage of water-refrigerant heat exchanger 12 , and high-temperature heat-medium pump 41 .

With the cycle configuration designed above, the control device 60 appropriately controls the operation of various control target devices in a manner similar to the cooling mode of the third embodiment.

Therefore, in the refrigeration cycle device 10b, in the cooling mode, a vapor compression cycle is configured in which the water-refrigerant heat exchanger 12 works as a condensation unit and the indoor evaporator 18 works as an evaporation unit. As a result, in the refrigeration cycle device 10b in the cooling mode, the heat medium can be heated by the water-refrigerant heat exchanger 12 . The blown air can be cooled by the internal evaporator 18 .

In the heat medium circuit 90, in the cooling mode, the heat medium heated by the water-refrigerant heat exchanger 12 flows into the radiator 92. The heat medium flowing into the radiator 92 exchanges heat with the outside air to give off heat to the outside air.

In the interior air conditioning unit 30, in the cooling mode, the blown air cooled by the interior evaporator 18 can be blown into the vehicle cabin. As a result, the vehicle cabin can be cooled.

In the refrigeration cycle device 10b in the cooling mode, the excess refrigerant in the cycle is stored in the receiver 23, so the ability to cool the blown air can be improved as in the third embodiment.

(2) Cooling and battery cooling mode

In the cooling and battery cooling mode, the controller 60 places the cabin cooling expansion valve 14b in a throttled state and the device cooling expansion valve 14c in a throttled state. The control device 60 controls the high-temperature heat-medium pump 41 and the low-temperature heat-medium pump 51 to have the predetermined pumping capacity.

The controller 60 controls the operation of the first three-way valve 91a to flow the heat medium discharged from the high-temperature heat medium pump 41 into the radiator 92 . The control device 60 controls the operation of the second three-way valve 91 b so that the medium discharged from the low-temperature heat medium pump 51 flows into the cooling water passage 80 a of the battery 80 .

Therefore, in the cooling and battery cooling mode, the refrigerant in the refrigeration cycle device 10b circulates in the order of the compressor 11, the water-refrigerant heat exchanger 12, the receiver 23, the fourth three-way junction 13d, the cabin cooling expansion valve 14b, the indoor evaporator 18, the integrated evaporation pressure adjusting valve 20 and the compressor 11. Further, the refrigerant circulates in the order of compressor 11, water-refrigerant heat exchanger 12, receiver 23, fourth three-way junction 13d, device cooling expansion valve 14c, cooler 19, integrated evaporating pressure adjusting valve 20 and compressor 11.

That is, in the refrigeration cycle device 10b, in the cooling and battery cooling mode, the refrigerant cycle is switched to a refrigerant cycle in which the indoor evaporator 18 and the radiator 19 are connected in parallel to flow refrigerant.

In the heat medium circuit 90, in the cooling and battery cooling mode, the heat medium circulates in the order of the high-temperature heat-medium pump 41, the radiator 92, the water passage of the water-refrigerant heat exchanger 12, and the high-temperature heat-medium pump 41. Further, the cycle is switched to a cycle in which the Medium is circulated in the order of low-temperature heat-medium pump 51, cooling water passage 80a of battery 80, radiator 19, and low-temperature heat-medium pump 51.

With the cycle configuration designed above, the control device 60 appropriately controls the operation of various control target devices in a manner similar to the cooling and battery cooling mode of the third embodiment.

Therefore, in the refrigeration cycle device 10b, in the cooling and battery cooling mode, a vapor compression refrigeration cycle is configured in which the water-refrigerant heat exchanger 12 works as a condensation unit and the indoor evaporator 18 and the radiator 19 work as evaporation units. As a result, in the refrigeration cycle device 10b in the cooling and battery cooling mode, the heat medium can be heated by the water-refrigerant heat exchanger 12 . The blown air can be cooled by the internal evaporator 18 . The heat medium can be cooled by the cooler 19 .

In the heat medium circuit 90, in the cooling and battery cooling mode, the heat medium heated by the water-refrigerant heat exchanger 12 flows into the radiator 92. The heat medium flowing into the radiator 92 exchanges heat with the outside air and releases heat to the outside air. The heat medium cooled by the radiator 19 flows into the cooling water passage 80a of the battery 80. As a result, the battery 80 can be cooled.

In the interior air conditioning unit 30, in the cooling and battery cooling mode, the blown air cooled by the interior evaporator 18 can be blown into the vehicle cabin. As a result, the vehicle cabin can be cooled.

In the cooling and battery cooling mode, the refrigerant evaporating pressure in the radiator 19 can be regulated to be either higher or lower than the refrigerant evaporating pressure in the indoor evaporator 18 by the action of the integrated evaporating pressure adjustment valve 20 . Therefore, the temperature of the heat medium flowing into the cooling water passage 80a can be regulated in a wide temperature range depending on how much heat the battery 80 or the like generates.

In the refrigeration cycle device 10b in the cooling and battery cooling mode, the excess refrigerant in the cycle is stored in the receiver 23, so the ability to cool the blown air and the ability to cool the battery 80 can be improved as in the third embodiment.

(3) First dehumidification and heating mode

In the first dehumidification and heating mode, the controller 60 controls the cabin cooling expansion valve 14b in a throttled state and the device cooling expansion valve 14c in a fully closed state. The control device 60 controls the high-temperature heat-medium pump 41 to have the predetermined pumping capacity. The control device 60 controls the operation of the first three-way valve 91 a to flow the heat medium discharged from the high-temperature heat medium pump 41 into the heater core 42 .

Therefore, in the refrigeration cycle device 10b, in the first dehumidifying and heating mode, the refrigerant cycle is switched to a refrigerant cycle in which the refrigerant is charged in the order of the compressor 11, the water-refrigerant heat exchanger 12, the receiver 23, the cabin cooling expansion valve 14b, the indoor evaporator 18, the integrated Evaporation pressure adjustment valve 20 and the compressor 11 circulates. In the heat medium circuit 90, in the first dehumidification and heating mode, it is switched to a circuit in which the heat medium circulates in the order of the high-temperature heat-medium pump 41, the heater core 42, the water passage of the water-refrigerant heat exchanger 12, and the high-temperature heat-medium pump 41.

With the cycle configuration designed above, the control device 60 appropriately controls the operation of various control target devices in a manner similar to the cooling mode of the third embodiment.

Therefore, in the refrigeration cycle device 10b, in the first dehumidification and heating mode, a vapor compression refrigeration cycle is configured in which the water-refrigerant heat exchanger 12 works as a condensation unit and the indoor evaporator 18 works as an evaporation unit. As a result, in the refrigeration cycle device 10b in the first dehumidifying and heating mode, the heating medium can be heated by the water-refrigerant heat exchanger 12 . The blown air can be cooled by the internal evaporator 18 .

In the heat medium circuit 90, in the first dehumidifying and heating mode, the heat medium heated by the water-refrigerant heat exchanger 12 flows into the heater core 42.

In the interior air conditioning unit 30, in the first dehumidifying and heating mode, part of the blown air cooled by the interior evaporator 18 is reheated by the heater core 42, and the blown air whose temperature has been controlled to approach the target blowing temperature TAO can enter the vehicle cabin to be blown. As a result, the vehicle cabin can be dehumidified and heated.

In the refrigeration cycle device 10b in the first dehumidifying and heating mode, the excess refrigerant in the cycle is stored in the receiver 23, so the ability to cool the blown air can be improved as in the third embodiment.

(4) Second parallel dehumidification mode (corresponds to the parallel dehumidification mode of the first embodiment)

In the second dehumidification and heating mode, the controller 60 places the cabin cooling expansion valve 14b in a throttled state and places the device cooling expansion valve 14c in a throttled state.

The control device 60 controls the high-temperature heat-medium pump 41 and the low-temperature heat-medium pump 51 to have the predetermined pumping capacity.

The control device 60 controls the operation of the first three-way valve 91 a so that the heat medium discharged from the high-temperature heat medium pump 41 flows into the heater core 42 . The control device 60 controls the operation of the second three-way valve 91 b so that the medium discharged from the low-temperature heat medium pump 51 flows into the radiator 92 .

Therefore, in the second parallel dehumidification mode, the refrigerant in the refrigeration cycle device 10b circulates in the order of the compressor 11, the water-refrigerant heat exchanger 12, the receiver 23, the fourth three-way joint 13d, the cabin cooling expansion valve 14b, the indoor evaporator 18, the integrated evaporating pressure adjustment valve 20, and the compressor 11. Further, the refrigerant circulates in the order of compressor 11, water-refrigerant heat exchanger 12, receiver 23, fourth three-way junction 13d, device cooling expansion valve 14c, chiller 19, integrated evaporating pressure adjusting valve 20, and compressor 11.

That is, in the refrigeration cycle device 10b, in the second parallel dehumidifying mode, the refrigerant cycle is switched to a refrigerant cycle in which the indoor evaporator 18 and the radiator 19 are connected in parallel to flow refrigerant.

In the heat medium circuit 90, in the second parallel dehumidification mode, the heat medium circulates in the order of the high-temperature heat-medium pump 41, the heater core 42, the water passage of the water-refrigerant heat exchanger 12, and the high-temperature heat-medium pump 41. Further, the cycle is switched to a cycle in which the medium in circulates in the order of low-temperature heat-medium pump 51, radiator 92, radiator 19, and low-temperature heat-medium pump 51.

With the cycle configuration designed above, the control device 60 suitably controls the operation of various control target devices. For example, the controller 60 controls the compressor 11 similarly to the parallel dehumidifying mode of the third embodiment. The other control devices are controlled in a manner similar to that in the cooling and battery cooling mode of the third embodiment.

Therefore, in the refrigeration cycle device 10b, in the second dehumidification and heating mode, a vapor compression refrigeration cycle is configured in which the water-refrigerant heat exchanger 12 works as a condensation unit and the indoor evaporator 18 and the radiator 19 work as evaporation units. As a result, in the refrigeration cycle device 10b in the second dehumidifying and heating mode, the heating medium can be heated by the water-refrigerant heat exchanger 12 . The blown air can be cooled by the internal evaporator 18 . The heat medium can be cooled by the cooler 19 .

In the heat medium circuit 90, in the second dehumidifying and heating mode, the heat medium heated by the water-refrigerant heat exchanger 12 flows into the heater core 42. The heat medium cooled by the radiator 19 flows into the radiator 92. The heat medium flowing into the radiator 92 exchanges heat with outside air to absorb heat from the outside air.

In the interior air conditioning unit 30, in the second dehumidification and heating mode, the blown air cooled by the interior evaporator 18 is heated again by the heater core 42, and the blown air whose temperature has been controlled to approach the target blowing temperature TAO can be blown into the vehicle cabin . As a result, the vehicle cabin can be dehumidified and heated.

Furthermore, in the second dehumidifying and heating mode, the refrigerant evaporating pressure in the radiator 19 can be regulated to be either higher or lower than the refrigerant evaporating pressure in the indoor evaporator 18 by the action of the integrated evaporating pressure adjustment valve 20 . As a result, the amount of heat that the heating medium in the radiator 92 absorbs from the outside air can be regulated depending on the target blowing temperature TAO, and thus the ability to heat the blowing air in the heater core 42 can be regulated in a wide range.

In the refrigeration cycle device 10b in the second parallel dehumidifying mode, the excess refrigerant in the cycle is stored in the receiver 23, so the amount of heat absorbed by the radiator 19 can be increased and the ability to heat the blown air can be improved. Furthermore, the amount of heat that the refrigerant in the indoor evaporator 18 absorbs can be increased, and thus the ability to cool the blown air can be improved.

(5) Outdoor air heating mode

In the outside air heating mode, the controller 60 places the cabin cooling expansion valve 14b in a fully closed state and the device cooling expansion valve 14c in a throttled state. The control device 60 controls the high-temperature heat-medium pump 41 and the low-temperature heat-medium pump 51 to have the predetermined pumping capacity.

The control device 60 controls the operation of the first three-way valve 91 a to flow the heat medium discharged from the high-temperature heat medium pump 41 into the heater core 42 . The control device 60 controls the operation of the second three-way valve 91 b so that the medium discharged from the low-temperature heat medium pump 51 flows into the radiator 92 .

Therefore, in the outdoor air heating mode, the refrigerant circulates in the refrigeration cycle device 10b in the order of the compressor 11, the water-refrigerant heat exchanger 12, the receiver 23, the device cooling expansion valve 14c, the chiller 19, the integrated evaporation pressure adjustment valve 20, and the compressor 11.

In the outdoor air heating mode, in the heat medium circuit 90, the heat medium circulates in the order of high-temperature heat-medium pump 41, radiator 92, water passage of the water-refrigerant heat exchanger 12, and high-temperature heat-medium pump 41. Furthermore, the circuit is switched to a circuit in which the medium is circulated in the order of low-temperature heat-medium pump 51, radiator 92, radiator 19 and low-temperature heat medium pump 51 circulates.

With the cycle configuration designed above, the control device 60 suitably controls the operation of various control target devices. For example, the throttle opening of the device cooling expansion valve 14c is controlled so that the superheat degree SHC of the refrigerant on the outlet port side of the radiator 19 approaches the target superheat degree SHCO. The other control devices are controlled in a manner similar to that in the outside air heating mode in the third embodiment.

Therefore, in the refrigeration cycle device 10b, in the outside air heating mode, a vapor compression refrigeration cycle is configured in which the water-refrigerant heat exchanger 12 works as a condensation unit and the radiator 19 works as an evaporation unit. As a result, in the refrigeration cycle device 10b in the outside air heating mode, the heating medium can be heated by the water-refrigerant heat exchanger 12 . The heat medium can be cooled by the cooler 19 . In other words, the refrigerant can absorb heat from the heat medium.

In the outside air heating mode, the heat medium heated by the water-refrigerant heat exchanger 12 in the heat medium circuit 90 flows into the heater core 42. The heat medium heated by the radiator 19 flows into the radiator 92. The heat medium flowing into the radiator 92 exchanges heat with the outside air, to absorb heat from the outside air.

In the interior air conditioning unit 30, in the outside air heating mode, blown air heated by the heater core 42 can be blown into the vehicle cabin. As a result, the vehicle cabin can be heated by using the heat received from the outside air as a heat source.

In the refrigeration cycle device 10b in the outside air heating mode, the refrigerant on the outlet port side of the radiator 19 may have the superheat degree. As a result, the amount of heat absorbed by the refrigerant in the radiator 19 can be increased, and hence the ability to heat the blown air can be improved, as in the third embodiment.

(7) Waste heat recovery and heating mode

In the waste heat recovery and heating mode, the controller 60 controls the cabin cooling expansion valve 14b in a fully closed state and the device cooling expansion valve 14c in a throttled state. The control device 60 controls the high-temperature heat-medium pump 41 and the low-temperature heat-medium pump 51 to have the predetermined pumping capacity.

The control device 60 controls the operation of the first three-way valve 91 a so that the heat medium discharged from the high-temperature heat medium pump 41 flows into the heater core 42 . The control device 60 controls the operation of the second three-way valve 91 b so that the medium discharged from the low-temperature heat medium pump 51 flows into the cooling water passage 80 a of the battery 80 .

Therefore, in the refrigeration cycle device 10b in the exhaust heat recovery and heating mode, the refrigerant circulates in the order of the compressor 11, the water-refrigerant heat exchanger 12, the receiver 23, the device cooling expansion valve 14c, the radiator 19, the integ rated evaporation pressure adjustment valve 20 and the compressor 11.

In the heat medium circuit 90, in the waste heat recovery and heating mode, the heat medium circulates in the order of the high-temperature heat-medium pump 41, the heater core 42, the water passage of the water-refrigerant heat exchanger 12, and the high-temperature heat-medium pump 41. Further, the cycle is switched to a cycle in which the heat medium circulated in the order of low-temperature heat-medium pump 51, cooling water passage 80a of battery 80, radiator 19, and low-temperature heat-medium pump 51.

With the cycle configuration designed above, the control device 60 controls the operation of the various control target devices in a manner similar to that in the outside air heating mode.

Therefore, in the refrigeration cycle device 10b, in the exhaust heat recovery and heating mode, a vapor compression cycle is configured in which the water-refrigerant heat exchanger 12 works as a condensation unit and the radiator 19 works as an evaporation unit. As a result, in the refrigeration cycle device 10 b in the exhaust heat recovery and heating mode, the heat medium can be heated by the water-refrigerant heat exchanger 12 . The heat medium can be cooled by the cooler 19 .

In the heat medium circuit 90, in the exhaust heat recovery and heating mode, the heat medium heated by the water-refrigerant heat exchanger 12 flows into the heater core 42. The heat medium cooled by the radiator 19 flows into the cooling water passage 80a of the battery 80. As a result, the battery 80 can be cooled. In other words, the heat medium can absorb the waste heat from the battery 80 .

In the interior air conditioning unit 30, in the exhaust heat recovery and heating mode, the blown air heated by the heater core 42 can be blown into the vehicle cabin. As a result, the vehicle cabin can be heated by using the heat received from the battery 80 as a heat source.

In the refrigeration cycle device 10b in the exhaust heat recovery and heating mode, the refrigerant at the outlet port side of the radiator 19 may have a degree of superheat. As a result, the amount of heat absorbed by the refrigerant in the radiator 19 can be increased, and thus the ability to heat blown air can be improved like in the outside air heating mode.

(8) battery cooling mode

In the battery cooling mode, the controller 60 places the cabin cooling expansion valve 14b in a fully closed state and the device cooling expansion valve 14c in a throttled state. The control device 60 controls the high-temperature heat-medium pump 41 and the low-temperature heat-medium pump 51 to have the predetermined pumping capacity.

The controller 60 controls the operation of the first three-way valve 91a to flow the heat medium discharged from the high-temperature heat medium pump 41 into the radiator 92 . The control device 60 controls the operation of the second three-way valve 91 b so that the heat medium discharged from the low-temperature heat medium pump 51 flows into the cooling water passage 80 a of the battery 80 .

Therefore, in the battery cooling mode, the refrigerant circulates in the refrigeration cycle device 10b in the order of the compressor 11, the water-refrigerant heat exchanger 12, the receiver 23, the device cooling expansion valve 14c, the radiator 19, the integrated evaporation pressure adjustment valve 20, and the compressor 11.

In the heat medium circuit 90 in the battery cooling mode, the heat medium circulates in the order of the high-temperature heat-medium pump 41, the radiator 92, the water passage of the water-refrigerant heat exchanger 12, and the high-temperature heat-medium pump 41. Further, the cycle is switched to a cycle in which the medium is in the order Low temperature heat medium pump 51, cooling water passage 80a of battery 80, radiator 19 and low temperature heat medium pump 51 circulates.

With the cycle configuration designed above, the control device 60 controls the operation of various control target devices in a manner similar to the battery cooling mode of the third embodiment.

Therefore, in the refrigeration cycle device 10b, in the battery cooling mode, a vapor compression refrigeration cycle is configured in which the water-refrigerant heat exchanger 12 works as a condensation unit and the radiator 19 works as an evaporation unit. As a result, in the refrigeration cycle device 10b in the outside air heating mode, the heating medium can be heated by the water-refrigerant heat exchanger 12 . The heat medium can be cooled by the cooler 19 .

In the heat medium circuit 90, in the battery cooling mode, the heat medium heated by the water-refrigerant heat exchanger 12 flows into the radiator 92. The heat medium flowing into the radiator 92 exchanges heat with the outside air and releases heat to the outside air. The heat medium cooled by the radiator 19 flows into the cooling water passage 80a of the battery 80. As a result, the battery 80 can be cooled.

In the refrigeration cycle device 10b in the battery cooling mode, the excess refrigerant in the cycle is stored in the receiver 23, so the amount of heat received by the radiator 19 can be increased and the ability to heat the blown air can also be improved.

As described above, the refrigeration cycle device 10b according to the present embodiment can switch various operation modes. As a result, the vehicle air conditioner 1 can perform comfortable air conditioning of the vehicle cabin while appropriately regulating the temperature of the battery 80 .

Also in the refrigeration cycle device 10b of the refrigeration cycle having two heat exchangers functioning as evaporation units according to the present embodiment, by using the integrated evaporation pressure adjustment valve 20, effects similar to those in the first embodiment can be obtained.

That is, the refrigerant evaporating temperature in one of a plurality of evaporating units connected in parallel with respect to a refrigerant flow can be appropriately controlled without being affected by the refrigerant evaporating temperature in another evaporating unit. Furthermore, the refrigerant evaporating temperatures in the plurality of evaporating units connected in parallel with each other can be appropriately controlled without complicating or increasing a circuit configuration.

The present disclosure is not limited to the above-described embodiments, and can be variously modified as follows without departing from the gist of the present disclosure.

The present embodiments have described an example in which the refrigeration cycle devices 10 to 10b are applied to a vehicle air conditioner mounted on an electric vehicle, but the present disclosure is not limited thereto. For example, the present disclosure can be applied to a vehicle air conditioner mounted on a so-called hybrid vehicle that obtains driving force for running the vehicle from both an internal combustion engine and an electric motor.

Furthermore, the present embodiments have described an example of cooling the battery 80 as a cooling target, but the present disclosure is not limited thereto. For example, an in-vehicle device that generates heat during operation, such as a travel electric motor that outputs driving power for travel, an inverter that supplies electric power to a electric motor, or a transaxle that is a power transmission mechanism, can be used as the cooling target .

Application of the refrigeration cycle devices 10 to 10b is not limited to a vehicle. In the present embodiments, the present disclosure can be applied to, for example, a stationary air conditioner that performs air conditioning in a computer server room. In this case, the computer server can be the cooling target.

The configurations of the refrigeration cycle devices 10 to 10b are not limited to the configurations disclosed in the embodiments.

For example, the above embodiments have described an example in which the heating unit that heats the blown air includes the individual components of the water-refrigerant heat exchanger 12 and the high-temperature-side heat medium circuit 40, but the present disclosure is not limited thereto. For example, as in 13 shown, the high-temperature-side heat medium circuit 40 is omitted and an internal condenser 121 is used.

The indoor condenser 121 is a heating heat exchanger that exchanges heat between the refrigerant discharged from the compressor 11 and the air blown into the vehicle cabin to heat the air blown. The indoor condenser 121 may be disposed in the case 31 of the indoor air conditioning unit 30, similarly to the heater core 42.

The above embodiments have described an example in which the cooling unit that cools the cooling target includes the individual components of the radiator 19 and the low-temperature-side heat medium circuit 50, but the present disclosure is not limited thereto. For example, as in 13 shown, the high-temperature-side heat medium circuit 40 is omitted, and the low-pressure refrigerant decompressed by the device refrigeration expansion valve 14c with tel can be fed directly into the cooling water passage 80a of the battery 80. In this case, the cooling water passage 80a works as a cooling heat exchange unit.

Alternatively, a cooling evaporator can also be used as an evaporation unit. The cooling evaporator is a cooling heat exchanger that exchanges heat between the low-pressure refrigerant decompressed by the device cooling expansion valve 14c and the cooling-blown air blown to the cooling target to cool the cooling-blown air.

In the first embodiment described above, the battery 80 is cooled and at the same time the waste heat of the battery 80 is recovered by cooling the low-temperature-side heat medium using the cooler 19, but the present disclosure is not limited to this. For example, a cooling heat exchanger that vaporizes the low-pressure refrigerant only for cooling the battery 80 and a heat-receiving heat exchanger that vaporizes the refrigerant only for the exhaust heat recovery of the battery 80 may be provided.

The present embodiments have described an example of using R1234yf as the refrigerant of the refrigeration cycle device 10, but the present disclosure is not limited thereto. For example, R134a, R600a, R410A, R404A, R32, R407C and the like can be used. Alternatively, a mixed refrigerant obtained by mixing a plurality of these refrigerants or the like can also be used.

The present embodiments have described an example of using an ethylene glycol aqueous solution as the heat medium of the high-temperature-side heat-medium circuit 40, the low-temperature-side heat-medium circuit 50, and the heat-medium circuit 90, but the present disclosure is not limited thereto. For example, a solution containing dimethylpolysiloxane, nanofluid or the like, a liquid antifreeze, an aqueous liquid refrigerant containing alcohol or the like, or a liquid medium containing oil or the like can be used.

The evaporation pressure adjustment unit is not limited to the integrated evaporation pressure adjustment valve 20, 210 disclosed in the exemplary embodiments. For example, the embodiments have described an example in which three inlet ports are provided, but an evaporation pressure adjustment unit having four or more inlet ports may also be used.

Furthermore, the integrated evaporation pressure adjustment valve 20, 210 may have an attachment portion to which a sensor for controlling the air conditioner is attached. Specifically, the attachment portion to which the second refrigerant temperature sensor 64b, the third refrigerant temperature sensor 64c, the second refrigerant temperature sensor 64b, the third refrigerant pressure sensor 65c, the fourth refrigerant pressure sensor 65d, or the like is attached may be included.

The devices disclosed in the individual embodiments can be appropriately combined within a realizable range.

For example, the integrated evaporation pressure adjustment valve 210 described in the second embodiment can be applied to the refrigeration cycle devices 10a and 10b described in the third and fourth embodiments.

For example, the indoor condenser 121 and the cooling evaporator described above can be applied to the refrigeration cycle device 10a described in the third embodiment.

Although the present disclosure has been described according to the examples, it should be understood that the present disclosure is not limited to the examples and structures. The present disclosure also includes various modifications and modifications within an equivalent range. Furthermore, various combinations and modes, and other combinations and modes including only one element, more elements, or fewer elements are also within the scope and spirit of the present disclosure.

QUOTES INCLUDED IN DESCRIPTION

This list of the documents cited by the applicant was generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Patent Literature Cited

• JP 2020017177 [0001]
• JP2012225637A [0006]

Claims (7)

Refrigeration cycle device comprising: a plurality of evaporation units (16, 18, 19) designed to evaporate a refrigerant; an evaporating pressure adjustment unit (20, 210) disposed downstream of the plurality of evaporating units in a refrigerant flow to regulate a refrigerant evaporating pressure in the plurality of evaporating units; and a refrigerant cycle switching unit (15a, 15b) configured to switch a refrigerant cycle, wherein the plurality of evaporation units has at least three evaporation units, when one of the plurality of evaporating units is defined as a first evaporating unit and another evaporating unit is defined as a second evaporating unit, the refrigerant cycle switching unit switches the refrigerant cycle such that the first evaporation unit and the second evaporation unit are connected in parallel to a refrigerant flow direction when the refrigerant is evaporated in the first evaporation unit and the second evaporation unit, and the evaporating pressure adjustment unit is capable of regulating a refrigerant evaporating pressure in the first evaporating unit to either a higher value or a lower value than a refrigerant evaporating pressure in the second evaporating unit. Refrigeration cycle device claim 1 , wherein when one of the plurality of evaporating units other than the first evaporating unit and the second evaporating unit is defined as a third evaporating unit, the refrigerant cycle switching unit connects the first evaporating unit, the second evaporating unit, and the third evaporating unit in parallel to a refrigerant flow direction when a refrigerant is evaporated in the first evaporation unit, the second evaporation unit and the third evaporation unit, and the evaporation pressure adjustment unit regulates a refrigerant evaporation pressure in the third evaporation unit to be equal to a low pressure of a refrigerant evaporation pressure in the first evaporation unit and a refrigerant evaporation pressure in the second evaporation unit. Refrigeration cycle device claim 2 wherein the refrigerant cycle switching unit comprises a blocking unit (14a to 14c) which blocks a flow of refrigerant into the third evaporating unit when the refrigerant is evaporated in the first evaporating unit and the second evaporating unit. Refrigeration cycle device according to any one of Claims 1 until 3 wherein the plurality of evaporating units comprises: an outdoor heat exchanger (16) exchanging heat between the refrigerant and the outdoor air, an indoor evaporator (18) exchanging heat between the refrigerant and the air blown into an air-conditioning target space, and a cooling heat exchange unit (19, 80a) evaporating the refrigerant to cool a cooling target (80). Refrigeration cycle device according to any one of Claims 1 until 4 wherein the evaporation pressure adjustment unit comprises: a single opening regulation unit (202, 212) that regulates passage cross-sectional areas of a plurality of refrigerant passages (201a to 201c, 211a to 211c) in which the refrigerant flowing out from the plurality of evaporating units flows, respectively, and a drive unit (203, 213) which moves the opening regulation unit. A refrigeration cycle device comprising: a plurality of evaporation units (16, 18, 19) configured to evaporate a refrigerant; and an evaporating pressure adjusting unit (20, 210) arranged downstream of the plurality of evaporating units in a refrigerant flow direction for regulating a refrigerant evaporating pressure in the plurality of evaporating units, wherein the evaporating units are connected in parallel with each other with respect to a refrigerant flow direction when one of the plurality of evaporating units is defined as a first evaporating unit and another evaporating unit is defined as a second evaporating unit, the evaporating pressure adjusting unit is capable of controlling a refrigerant evaporating pressure in the first evaporating unit to either a higher value or a lower value than a refrigerant evaporating pressure in the second evaporating unit regulate, and the evaporating pressure adjusting unit comprises a single opening regulating unit (202, 212), the passage cross-sectional areas of a plurality of refrigerants Medium passages (201a to 201c, 211a to 211c) regulated in which the refrigerant from the lot number of evaporation units, respectively, and a driving unit (203, 213) which moves the opening regulation unit. Refrigeration cycle device according to any one of Claims 1 until 6 further comprising a compressor (11) that compresses and discharges a refrigerant flowing out from said evaporating pressure adjustment unit, said evaporating pressure adjustment unit having a reverse flow preventing function that prevents the refrigerant from flowing from a suction port of said compressor toward said plurality of evaporating units .

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