JP2020139680A - Refrigeration cycle device - Google Patents

Abstract

To provide a refrigeration cycle device which can distribute refrigerants to a plurality of evaporators which are connected to one another in parallel with one another at a prescribed ratio while suppressing the deterioration of mountability.SOLUTION: A refrigeration cycle device 10 comprises a compressor 11, a heat radiator 12, a cooling decompression part 14, a cooling evaporator 15, a first battery decompression part 16, a first battery evaporator 17, a second battery decompression part 18 and a second battery evaporator 19. Each of the decompression parts 14, 16 and 18 includes a microvalve for making a throttle opening variable. The microvalve has a drive part which is displaced by a temperature change, an amplification part for amplifying the displacement of the drive part caused by the temperature change, and a movable part for adjusting a flow rate of a refrigerant flowing in each of the decompression part 14, 16 and 18 by moving by being transmitted with displacement amplified by the amplification part. The amplification part is constituted so as to function as a lever with a hinge as a pivot, with an energization position in which the amplification part is energized by the drive part as a power point, and with a connecting position between the amplification part and the movable part as a point of action.SELECTED DRAWING: Figure 1

Description

The present disclosure relates to a vapor compression refrigeration cycle apparatus.

Conventionally, there is known a refrigeration cycle device in which an evaporator for air cooling provided with an expansion valve and a battery cooler provided with an expansion valve are connected in parallel on the downstream side of an outdoor heat exchanger (for example, patent documents). 1). The battery cooler is composed of a plurality of evaporators connected in parallel on the downstream side of the expansion valve. A distributor for distributing the gas-liquid two-phase refrigerant that has passed through the expansion valve is provided between the expansion valve and the plurality of evaporators, and the distributor provides the gas-liquid two-phase to the plurality of evaporators. The refrigerant is distributed.

Japanese Unexamined Patent Publication No. 2012-11146

By the way, it is technically very difficult to evenly distribute a gas-liquid two-phase refrigerant including a gas refrigerant and a liquid refrigerant to a plurality of evaporators, and the liquid refrigerant inevitably flows into some evaporators in a biased manner. It ends up. When the liquid refrigerant flows unevenly into a part of a plurality of evaporators, the cell close to one of the evaporators of the battery becomes cold, and the cell close to the other evaporator becomes difficult to cool. Battery performance depends on poorly performing cells. Therefore, when a temperature distribution occurs in the battery, the battery performance deteriorates.

As a countermeasure, an electric expansion valve for driving the valve body by an electric motor such as a stepping motor is arranged on the upstream side of each of the plurality of evaporators, and the refrigerant flowing to the plurality of evaporators is evenly distributed by the electric expansion valve. It is conceivable to adjust to the flow rate.

However, the physique of the electric expansion valve becomes very large due to the electric motor. This is not preferable because it causes deterioration of mountability.

An object of the present disclosure is to provide a refrigeration cycle apparatus capable of distributing a refrigerant in a desired ratio to a plurality of evaporators connected in parallel while suppressing deterioration of mountability.

The invention according to claim 1
It is a refrigeration cycle device
A compressor (11) that compresses and discharges the refrigerant,
A radiator (12) that dissipates heat from the refrigerant discharged from the compressor,
On the downstream side of the refrigerant flow of the radiator, a plurality of decompression units (14, 16, 18) connected in parallel with each other,
A plurality of evaporators (15, 17, 19), which are connected to the downstream side of the refrigerant flow of each of the plurality of decompression units and evaporate the refrigerant decompressed by the decompression unit, are provided.
At least one of the plurality of decompression units is a variable decompression unit (14, 16, 18) including a valve component (X1) for adjusting the throttle opening degree.
Valve parts
The bases (X11, X12, X13) where a fluid chamber (X19) through which at least a part of the refrigerant that has passed through the radiator flows flows, and
Drive units (X123, X124, X125) that displace when their temperature changes,
Amplifying units (X126, X127) that amplify the displacement due to changes in the temperature of the driving unit,
It has a movable part (X128) that adjusts the pressure of the refrigerant in the fluid chamber by transmitting and moving the displacement amplified by the amplification part.
When the drive unit is displaced due to a change in temperature, the drive unit biases the amplification unit at the urging position (XP2), so that the amplification unit is displaced with the hinge (XP0) as a fulcrum, and the amplification unit and the movable unit are displaced. At the connection position (XP3), the amplification part urges the movable part,
A refrigeration cycle device in which the distance from the hinge to the connection position is longer than the distance from the hinge to the urging position.

According to this, since at least one of the plurality of decompression portions has a configuration in which the throttle opening can be changed, it is easy to distribute the refrigerant containing refrigerating machine oil to the plurality of evaporators at a desired ratio. Become. In addition, the amplification section of the valve component functions as a lever. Therefore, the amount of displacement corresponding to the temperature change of the driving unit is amplified by the lever and transmitted to the moving unit. In this way, the valve component whose displacement amount due to thermal expansion is amplified by using a lever can be configured to be smaller than that of a solenoid valve or an electric valve that does not use such a lever.

Therefore, according to the refrigeration cycle apparatus of the present disclosure, it is possible to distribute the refrigerant at a desired ratio to a plurality of evaporators connected in parallel while suppressing deterioration of mountability.

The invention according to claim 4
It is a refrigeration cycle device
A compressor (11) that compresses and discharges the refrigerant,
A radiator (12) that dissipates heat from the refrigerant discharged from the compressor,
On the downstream side of the refrigerant flow of the radiator, a plurality of decompression units (14, 16, 18) connected in parallel with each other,
A plurality of evaporators (15, 17, 19), which are connected to the downstream side of the refrigerant flow of each of the plurality of decompression units and evaporate the refrigerant decompressed by the decompression unit, are provided.
At least one of the plurality of decompression units is a variable decompression unit (14, 16, 18) whose throttle opening degree can be adjusted.
The variable decompression unit
Passes through the inlet flow path (281) into which the refrigerant that has passed through the radiator flows, the valve chamber (283) that communicates with the inlet flow path, the throttle flow path (284) that reduces and expands the refrigerant that has flowed into the valve chamber, and the throttle flow path. A block body (28) having an outlet flow path (282) for discharging the generated refrigerant toward the evaporator.
A main valve body (285) housed in the valve chamber and adjusting the throttle opening in the throttle flow path,
Includes a drive member (X0) that drives the main valve body,
The block body is formed with an opening degree adjusting chamber (286) into which a refrigerant for pressing the main valve body to the valve opening side or the valve closing side is introduced.
The drive member includes a valve component (Y1) for adjusting the pressure in the opening adjustment chamber.
Valve parts
The bases (Y11, Y12, Y13) on which the fluid chamber (Y19) through which the refrigerant introduced into the opening adjustment chamber flows flows, and
Drive units (Y123, Y124, Y125) that displace when their temperature changes,
Amplifying units (Y126, Y127) that amplify the displacement due to changes in the temperature of the driving unit,
It has a movable part (Y128) that adjusts the pressure of the refrigerant flowing through the fluid chamber by transmitting and moving the displacement amplified by the amplification part.
When the drive unit is displaced due to a change in temperature, the drive unit biases the amplification unit at the urging position (YP2), so that the amplification unit is displaced with the hinge (YP0) as a fulcrum, and the amplification unit and the movable unit are displaced. At the connection position (YP3) of, the amplification part urges the movable part,
A refrigeration cycle device in which the distance from the hinge to the connection position is longer than the distance from the hinge to the urging position.

According to this, by adjusting the pressure in the opening adjustment chamber by the valve parts, the main valve body can be displaced to the valve opening side or the valve closing side, so that the throttle opening of the variable decompression unit can be changed. It becomes easy to distribute the refrigerant containing the refrigerating machine oil to the evaporator at a desired ratio. In addition, the amplification section of the valve component functions as a lever. Therefore, the amount of displacement corresponding to the temperature change of the driving unit is amplified by the lever and transmitted to the moving unit. In this way, the valve component whose displacement amount due to thermal expansion is amplified by using a lever can be configured to be smaller than that of a solenoid valve or an electric valve that does not use such a lever.

The reference reference numerals in parentheses attached to each component or the like indicate an example of the correspondence between the component or the like and the specific component or the like described in the embodiment described later.

It is a schematic block diagram of the refrigeration cycle apparatus which concerns on 1st Embodiment. It is a block diagram which shows the electronic control part of the refrigeration cycle apparatus which concerns on 1st Embodiment. It is a schematic perspective view which shows the appearance of the decompression part for the 1st battery of the refrigeration cycle apparatus which concerns on 1st Embodiment. It is a schematic cross-sectional view of the decompression part for the 1st battery of the refrigeration cycle apparatus which concerns on 1st Embodiment. It is a schematic disassembled perspective view of the micro valve used for the decompression part for the 1st battery of the refrigeration cycle apparatus which concerns on 1st Embodiment. It is a schematic side view of the micro valve used for the 1st battery decompression part of the refrigeration cycle apparatus which concerns on 1st Embodiment. FIG. 6 is a cross-sectional view of VII-VII of FIG. 6, showing a closed state of the microvalve. It is sectional drawing which shows the VIII-VIII cross section of FIG. FIG. 6 shows a cross section of VII-VII of FIG. 6, which is a cross-sectional view showing a valve opened state of the microvalve. It is sectional drawing which shows the XX cross section of FIG. It is explanatory drawing for demonstrating operation of the decompression part for the 1st battery of the refrigeration cycle apparatus which concerns on 1st Embodiment. It is a schematic block diagram of the refrigeration cycle apparatus which concerns on 2nd Embodiment. It is a schematic cross-sectional view of the decompression part for the 1st battery of the refrigeration cycle apparatus which concerns on 3rd Embodiment. It is explanatory drawing for demonstrating operation of the decompression part for the 1st battery of the refrigeration cycle apparatus which concerns on 3rd Embodiment. It is explanatory drawing for demonstrating the relationship between the evaporator for 1st battery and the decompression part for 1st battery of the refrigerating cycle apparatus which concerns on 4th Embodiment. It is a schematic cross-sectional view which shows the decompression part for the 1st battery of the refrigeration cycle apparatus which concerns on 4th Embodiment. It is a schematic cross-sectional view which shows the decompression part for the 1st battery of the refrigeration cycle apparatus which concerns on 5th Embodiment, and shows the state which the throttle opening degree is the maximum. It is a schematic cross-sectional view which shows the 1st battery decompression part of the refrigeration cycle apparatus which concerns on 5th Embodiment, and shows the state which the throttle opening degree is the minimum. It is explanatory drawing for demonstrating the relationship between the control pressure of the decompression part for the 1st battery of the refrigerating cycle apparatus which concerns on 5th Embodiment, and the throttle opening degree. It is a schematic disassembled perspective view of the micro valve used for the decompression part for the 1st battery of the refrigeration cycle apparatus which concerns on 5th Embodiment. It is a schematic side view of the micro valve used for the 1st battery decompression part of the refrigeration cycle apparatus which concerns on 5th Embodiment. FIG. 21 is a cross-sectional view showing a cross section of XXII-XXII of FIG. 21, showing a non-energized state of the microvalve. It is sectional drawing which shows the cross section of XXIII-XXIII of FIG. FIG. 21 is a cross-sectional view showing a cross section of XXII-XXII of FIG. 21, showing a state of energization of the microvalve. It is sectional drawing which shows the cross section of XXV-XXV of FIG. It is explanatory drawing for demonstrating operation of the decompression part for the 1st battery of the refrigeration cycle apparatus which concerns on 5th Embodiment. It is a schematic diagram which shows the inside of the micro valve used for the 1st battery decompression part of the refrigerating cycle apparatus which concerns on 6th Embodiment. It is an enlarged view which enlarged a part of FIG. 27. It is a schematic diagram which shows the inside of the micro valve used for the 1st battery decompression part of the refrigeration cycle apparatus which concerns on 7th Embodiment. It is an enlarged view which enlarged a part of FIG.

Hereinafter, embodiments of the present disclosure will be described with reference to the drawings. In the following embodiments, the same reference numerals may be assigned to parts that are the same as or equivalent to those described in the preceding embodiments, and the description thereof may be omitted. Further, when only a part of the component is described in the embodiment, the component described in the preceding embodiment can be applied to the other part of the component. The following embodiments can be partially combined with each other as long as the combination does not cause any trouble, even if not explicitly stated.

(First Embodiment)
This embodiment will be described with reference to FIGS. 1 to 11. In the present embodiment, an example in which the refrigeration cycle device 10 of the present disclosure is applied to an electric vehicle in which a driving force for traveling a vehicle is obtained from an electric motor will be described.

The electric vehicle is equipped with a battery BT that stores electric power supplied to an electric motor for traveling. The battery BT is configured as a rechargeable secondary battery. Specifically, the battery BT is composed of a plurality of battery modules M1 and M2 electrically connected in series. The battery BT of the present embodiment is composed of a first battery module M1 and a second battery module M2. Each battery module M1 and M2 is composed of a series connector in which a plurality of cells C are electrically connected in series.

The battery BT generates heat when supplying electric power to an electric motor for traveling. If the temperature of the battery BT rises excessively, the battery BT deteriorates or the output is limited. Therefore, the battery BT needs to be appropriately cooled so that its temperature is maintained below a predetermined reference temperature (for example, 50 ° C.).

In consideration of such a background, in the present embodiment, the air supplied to the vehicle interior and the battery BT are targeted for cooling of the refrigeration cycle device 10. That is, the refrigeration cycle device 10 is configured to adjust each of the air supplied to the vehicle interior and the battery BT to a desired temperature.

As shown in FIG. 1, the refrigeration cycle device 10 includes a compressor 11, a radiator 12, a decompression unit 14 for cooling, an evaporator 15 for cooling, a decompression unit 16 for a first battery, an evaporator 17 for a first battery, and a first. A pressure reducing unit 18 for two batteries, an evaporator 19 for a second battery, and a pressure adjusting valve 20 are provided. Each of these constituent devices is connected by a refrigerant pipe. Further, the refrigeration cycle device 10 includes a control device 100 that controls the operation of each component device.

The refrigeration cycle device 10 employs an HFC-based refrigerant (specifically, R134a) as the refrigerant. Refrigerant oil for lubricating the compressor 11 is mixed in the refrigerant, and a part of the refrigerating machine oil circulates in a cycle together with the refrigerant. As the refrigerant, an HFO-based refrigerant (for example, R1234yf), a natural refrigerant (for example, R744), or the like may be adopted.

The compressor 11 sucks in the refrigerant, compresses it, and discharges it in the refrigeration cycle device 10. The compressor 11 is composed of an electric compressor that drives a fixed-capacity compression mechanism with a fixed discharge capacity by an electric motor. The compressor 11 is arranged inside the hood of the vehicle. The operation (for example, rotation speed) of the electric motor constituting the compressor 11 is controlled by a control signal output from the control device 100.

The refrigerant inlet side of the radiator 12 is connected to the refrigerant discharge side of the compressor 11. The radiator 12 is a heat exchanger that dissipates heat from the refrigerant discharged from the compressor 11. Specifically, the radiator 12 includes a refrigerant flow path portion 121 through which the refrigerant flows and a heat medium flow path portion 122 through which the heat medium of the heater circuit HC flows, and heats the refrigerant and the heat medium flowing through the heater circuit HC. It constitutes a heat exchanger for heating that is exchanged to heat a heat medium. The heater circuit HC is a circuit for being used as a heat source for heating the blown air that blows the refrigerant discharged from the compressor 11 into the vehicle interior, warming up the battery BT, and the like. Although not shown, the heater circuit HC is provided with a heater core for dissipating heat to the air blown into the vehicle interior, a radiator for dissipating heat to the battery BT, and the like.

A cooling pressure reducing unit 14 is connected to the refrigerant outlet side of the radiator 12. The cooling decompression unit 14 is a decompression unit that decompresses the refrigerant that has passed through the radiator 12 during air conditioning in the vehicle interior. The cooling decompression unit 14 is configured in the same manner as the first battery decompression unit 16 described later. Therefore, the description of the cooling pressure reducing unit 14 will be omitted.

The refrigerant inlet portion 150 of the cooling evaporator 15 is connected to the refrigerant outlet side of the cooling decompression unit 14. The cooling evaporator 15 is an evaporator that evaporates the refrigerant decompressed by the cooling decompression unit 14. The cooling evaporator 15 is arranged inside an air conditioning case (not shown), and heat-exchanges the refrigerant with the air blown from the indoor fan 151 to evaporate the refrigerant. In other words, the cooling evaporator 15 is an air cooler that cools the air blown from the indoor fan 151 by exchanging heat with the refrigerant. The indoor fan 151 is a blower that blows the air cooled by the cooling evaporator 15 into the vehicle interior.

Here, the refrigerating cycle device 10 is connected to the decompression unit 16 for the first battery and the decompression unit 18 for the second battery so as to be parallel to the decompression unit 14 for cooling on the refrigerant outlet side of the radiator 12. .. Specifically, a first branch portion 21 is provided between the radiator 12 and the cooling pressure reducing portion 14. The first branch portion 21 is for allowing a part of the refrigerant flowing from the radiator 12 toward the cooling decompression section 14 to flow toward the first battery decompression section 16 and the second battery decompression section 18.

Further, on the downstream side of the refrigerant flow of the first branch portion 21, the second branch portion 22 for distributing the refrigerant branched at the first branch portion 21 to the decompression unit 16 for the first battery and the decompression unit 18 for the second battery. Is provided. A first battery decompression unit 16 is connected to one of the refrigerant outlets, and a second battery decompression unit 18 is connected to the other refrigerant outlet side of the second branch 22.

The decompression unit 16 for the first battery is a decompression unit that decompresses the refrigerant flowing in through the branch portions 21 and 22 when the battery BT is cooled. The first battery decompression unit 16 is configured as a variable diaphragm whose throttle opening degree can be changed. The details of the decompression unit 16 for the first battery will be described later.

A refrigerant inlet 170 of the first battery evaporator 17 is connected to the refrigerant outlet side of the first battery decompression unit 16. The first battery evaporator 17 is an evaporator that evaporates the refrigerant decompressed by the first battery decompression unit 16. The first battery evaporator 17 is a heat absorber that absorbs heat from the first battery module M1 of the battery BT to evaporate the refrigerant. In other words, the first battery evaporator 17 is a battery cooler that cools the first battery module M1 by heat exchange with the refrigerant.

The second battery decompression unit 18 is a decompression unit that decompresses the refrigerant flowing in through the branch portions 21 and 22 when the battery BT is cooled. Since the decompression unit 18 for the second battery has the same configuration as the decompression unit 16 for the first battery, the description of the decompression unit 18 for the second battery will be omitted.

The refrigerant inlet 190 of the second battery evaporator 19 is connected to the refrigerant outlet side of the second battery decompression unit 18. The second battery evaporator 19 is an evaporator that evaporates the refrigerant decompressed by the second battery decompression unit 18. The second battery evaporator 19 is a heat absorber that absorbs heat from the second battery module M2 of the battery BT to evaporate the refrigerant. In other words, the second battery evaporator 19 is a battery cooler that cools the second battery module M2 by exchanging heat with the refrigerant.

The refrigerant that has passed through the first battery evaporator 17 and the refrigerant that has passed through the second battery evaporator 19 merge on the downstream side of the refrigerant flow of each of the first battery evaporator 17 and the second battery evaporator 19. A first confluence 23 is provided. Further, on the downstream side of the refrigerant flow of the first merging portion 23, a second merging portion 24 is provided for merging the refrigerant merged at the first merging portion 23 and the refrigerant that has passed through the cooling evaporator 15. The downstream side of the refrigerant flow of the second confluence 24 is connected to the refrigerant suction side of the compressor 11.

Here, a pressure adjusting valve 20 is arranged between the first merging portion 23 and the second merging portion 24. The pressure regulating valve 20 maintains the pressure of the refrigerant passing through the first battery evaporator 17 and the second battery evaporator 19 at a predetermined set pressure value or higher. The pressure regulating valve 20 is composed of, for example, a bellows type evaporation pressure regulating valve.

Since the refrigerating cycle device 10 is provided with the pressure adjusting valve 20, for example, when cooling the battery BT and cooling the vehicle interior at the same time, the pressure of the refrigerant passing through the evaporators 17 and 19 for each battery is maintained. While doing so, the pressure of the refrigerant passing through the cooling evaporator 15 can be reduced.

Next, the control device 100 constituting the electronic control unit of the refrigeration cycle device 10 will be described with reference to FIG. As shown in FIG. 2, the control device 100 includes a microcomputer including a memory such as a processor, a ROM, and a RAM, and peripheral circuits thereof. The memory of the control device 100 is composed of a non-transitional substantive storage medium.

An air conditioning sensor 101 and a battery sensor 102 are connected to the input side of the control device 100. The air conditioning sensor 101 is composed of a plurality of types of sensors used for controlling the cooling process. The air conditioning sensor 101 is, for example, a temperature sensor (such as an evaporator temperature sensor) that detects the refrigerant temperature on the low pressure side of the cycle, a high pressure sensor that detects the refrigerant pressure on the high pressure side of the cycle, and a temperature sensor that detects the temperature of the high pressure refrigerant. Includes. The battery sensor 102 is composed of a plurality of types of sensors used for controlling the cooling process of the battery BT. The battery sensor 102 includes, for example, a temperature sensor that detects the battery temperature of each of the battery modules M1 and M2.

The control device 100 performs various arithmetic processes based on various information acquired from the air conditioning sensor 101 and the battery sensor 102 and a control program stored in the memory, and controls the operation of each component device connected to the output side. To do.

Specifically, the compressor 11, the decompression unit 14 for cooling, the indoor fan 151, the decompression unit 16 for the first battery, and the decompression unit 18 for the second battery are connected to the output side of the control device 100. The control device 100 can adjust the refrigerant discharge performance (for example, refrigerant pressure) by the compressor 11, the throttle opening degrees of the decompression units 14, 16 and 18, and the ventilation performance of the indoor fan 151 according to the situation. That is, in the refrigeration cycle device 10, the control device 100 desires the air and the battery BT to be supplied to the vehicle interior by controlling the operations of the compressor 11, the decompression units 14, 16, 18 and the indoor fan 151, respectively. It can be adjusted to the temperature of.

In particular, the refrigeration cycle device 10 is provided with a pressure adjusting valve 20 on the downstream side of the refrigerant flow of the first battery evaporator 17 and the second battery evaporator 19. According to this, for example, when cooling the battery BT and cooling the passenger compartment at the same time, the refrigerant passing through the cooling evaporator 15 is maintained while maintaining the pressure of the refrigerant passing through the battery evaporators 17 and 19. The pressure can be reduced.

Further, the refrigeration cycle device 10 corresponds to the cooling evaporator 15, the first battery evaporator 17, and the second battery evaporator 19, respectively, and corresponds to the cooling decompression unit 14, the first battery decompression unit 16, and the first. A decompression unit 18 for two batteries is provided. According to this, as compared with the conventional technique in which the gas-liquid two-phase refrigerant containing the gas refrigerant and the liquid refrigerant after passing through the decompression section is distributed to a plurality of evaporators, the evaporators 15 and 17 are respectively. , A gas-liquid two-phase refrigerant containing a gas refrigerant and a liquid refrigerant can be appropriately distributed with respect to 19. As a result, it is possible to suppress a decrease in battery performance due to the temperature distribution in the battery BT. Further, with the above configuration, the refrigerating machine oil contained in the refrigerant is also distributed to the evaporators 15, 17 and 19, so that the refrigerating machine oil is unevenly distributed to some evaporators and the compressor. It is possible to suppress the occurrence of poor lubrication of 11.

Here, the cooling decompression unit 14, the decompression unit 16 for the first battery, and the decompression unit 18 for the second battery are electric motors such as a solenoid valve for driving the valve body with a solenoid actuator and a stepping motor for driving the valve body. It is conceivable that the configuration includes a valve.

However, in this case, it is necessary to use a large actuator, and the refrigeration cycle device 10 becomes large. In particular, in the refrigeration cycle apparatus 10 of the present embodiment, since the decompression portions 14, 16 and 18 are provided corresponding to the evaporators 15, 17 and 19, respectively, the size of the refrigeration cycle apparatus 10 is significantly increased. It becomes.

In consideration of these factors, in the refrigeration cycle apparatus 10 of the present disclosure, each of the decompression units 14, 16 and 18 is composed of a valve module X0 including a microvalve X1. The micro valve X1 is a valve component for varying the throttle opening of each of the pressure reducing portions 14, 16 and 18. In the present embodiment, each of the decompression units 14, 16 and 18 corresponds to the variable decompression unit, and each of the evaporators 15, 17 and 19 corresponds to the variable evaporator. Further, the micro valve X1 is a valve component for varying the throttle opening degree of each of the pressure reducing portions 14, 16 and 18.

As described above, the decompression units 14, 16 and 18 have the same basic configuration. Therefore, in the present embodiment, the configuration of the decompression unit 16 for the first battery and the like will be described, and the description of the decompression unit 14 for cooling and the decompression unit 18 for the second battery will be omitted.

As shown in FIGS. 3 and 4, the valve module X0 is integrally configured with the block body 27 provided in the refrigerant pipe 26 connecting the second branch portion 22 and the first battery evaporator 17. ing. The block body 27 constitutes an object to be attached to be attached to the micro valve X1.

The block body 27 constitutes a part of the decompression unit 16 for the first battery. The block body 27 is a metal connected to an upstream portion 261 connected to the refrigerant outlet portion of the radiator 12 and a downstream portion 262 connected to the refrigerant inlet portion 170 of the first battery evaporator 17 in the refrigerant pipe 26. It is a joint made of (for example, aluminum).

A bottomed upstream fitting hole 271 into which the upstream portion 261 is fitted is formed on one side surface of the block body 27. Further, the block body 27 is formed with a bottomed downstream fitting hole 272 into which the downstream portion 262 is fitted on the opposite side of one side surface on which the upstream fitting hole 271 is formed. The upstream fitting hole 271 and the downstream fitting hole 272 are communicated with each other by an orifice 273. The orifice 273 is composed of through holes penetrating the bottoms of the fitting holes 271 and 272. The orifice 273 is composed of micropores so as to function as a fixed throttle that exerts a depressurizing action when the refrigerant flows.

Further, on the upper surface of the block body 27, a first recess 274 and a second recess 275 into which the first protrusion X21 and the second protrusion X22 of the valve module X0 described later are fitted are formed. At the bottom of the first recess 274, a through hole 274a is formed to communicate the first recess 274 and the upstream fitting hole 271. Further, a through hole 275a for communicating the second recess 275 and the downstream fitting hole 272 is formed at the bottom of the second recess 275.

[Configuration of valve module X0]
Hereinafter, the configuration of the valve module X0 will be described. As shown in FIG. 4, the valve module X0 has a microvalve X1, a valve casing X2, a sealing member X3, two O-rings X4, X5, and two electrical wires X6, X7.

The micro valve X1 is a plate-shaped valve component, and is mainly composed of a semiconductor chip. The microvalve X1 may or may not have parts other than the semiconductor chip. Therefore, the micro valve X1 can be made compact. The length of the microvalve X1 in the thickness direction is, for example, 2 mm, the length in the longitudinal direction orthogonal to the thickness direction is, for example, 10 mm, and the length in the lateral direction orthogonal to both the longitudinal direction and the thickness direction. Is, for example, 5 mm, but is not limited thereto. By switching between energization and non-energization of the micro valve X1, opening and closing is switched. Specifically, the micro valve X1 is a normally closed valve that opens when energized and closes when not energized.

The electrical wirings X6 and X7 extend from the surface of the two plates on the front and back of the microvalve X1 opposite to the valve casing X2, pass through the sealing member X3 and the valve casing X2, and pass through the valve module. It is connected to a power supply outside X0. As a result, electric power is supplied from the power source to the micro valve X1 through the electric wires X6 and X7.

The valve casing X2 is a resin casing that houses the microvalve X1. The valve casing X2 is formed by resin molding containing polyphenylene sulfide as a main component. The valve casing X2 is configured such that the coefficient of linear expansion is a value between the coefficient of linear expansion of the microvalve X1 and the coefficient of linear expansion of the block body 27. The valve casing X2 constitutes a component mounting portion for mounting the microvalve X1 to the block body 27.

The valve casing X2 is a concave box body having a bottom wall on one side and an open side on the other side. The bottom wall of the valve casing X2 is interposed between the block body 27 and the micro valve X1 so that the micro valve X1 and the block body 27 do not come into direct contact with each other. Then, one surface of the bottom wall is in contact with and fixed to the block body 27, and the other surface is in contact with and fixed to one of the two plate surfaces of the micro valve X1. In this way, the valve casing X2 can absorb the difference in the coefficient of linear expansion between the micro valve X1 and the block body 27. This is because the linear expansion coefficient of the valve casing X2 is a value between the linear expansion coefficient of the micro valve X1 and the linear expansion coefficient of the block body 27.

Further, the bottom wall of the valve casing X2 has a plate-shaped base portion X20 facing the micro valve X1 and a pillar-shaped first protruding portion X21 and a second protruding portion X21 protruding from the base portion X20 in a direction away from the micro valve X1. It has a part X22.

The first protruding portion X21 and the second protruding portion X22 are fitted into the first recess 274 and the second recess 275 formed in the block body 27. The first protruding portion X21 is formed with a first communication hole XV1 that penetrates from the end on the side of the micro valve X1 to the end on the bottom side of the first recess 274. The second protrusion X22 is formed with a second communication hole XV2 that penetrates from the microvalve X1 side end to the bottom side end of the second recess 275.

The sealing member X3 is a member made of epoxy resin that seals the other open side of the valve casing X2. The sealing member X3 covers the plate surface of the two plate surfaces on the front and back surfaces of the micro valve X1 on the side opposite to the bottom wall side of the valve casing X2. Further, the sealing member X3 covers the electric wirings X6 and X7 to realize waterproofing and insulation of the electric wirings X6 and X7. The sealing member X3 is formed by resin potting or the like.

The O-ring X4 is attached to the outer periphery of the first protruding portion X21 and seals between the block body 27 and the first protruding portion X21 to suppress leakage of the refrigerant to the outside of the decompression unit 16 for the first battery. To do. The O-ring X5 is attached to the outer periphery of the second protruding portion X22 and seals between the block body 27 and the second protruding portion X22 to suppress the leakage of the refrigerant to the outside of the decompression unit 16 for the first battery. To do.

[Configuration of micro valve X1]
Here, the configuration of the micro valve X1 will be further described. As shown in FIGS. 5 and 6, the microvalve X1 is a MEMS having a first outer layer X11, an intermediate layer X12, and a second outer layer X13, all of which are semiconductors. MEMS is an abbreviation for Micro Electro Mechanical Systems. The first outer layer X11, the intermediate layer X12, and the second outer layer X13 are rectangular plate-shaped members having the same outer shape, and are laminated in the order of the first outer layer X11, the intermediate layer X12, and the second outer layer X13. Of the first outer layer X11, the intermediate layer X12, and the second outer layer X13, the second outer layer X13 is arranged on the side closest to the bottom wall of the valve casing X2. The structures of the first outer layer X11, the intermediate layer X12, and the second outer layer X13, which will be described later, are formed by a semiconductor manufacturing process such as chemical etching.

The first outer layer X11 is a conductive semiconductor member having a non-conductive oxide film on its surface. As shown in FIG. 5, the first outer layer X11 is formed with two through holes X14 and X15 penetrating the front and back surfaces. The microvalve X1 side ends of the electrical wirings X6 and X7 are inserted into the through holes X14 and X15, respectively.

The second outer layer X13 is a conductive semiconductor member having a non-conductive oxide film on its surface. As shown in FIGS. 5, 7, and 8, the second outer layer X13 is formed with a first refrigerant hole X16 and a second refrigerant hole X17 penetrating the front and back surfaces. As shown in FIG. 7, the first refrigerant hole X16 communicates with the first communication hole XV1 of the valve casing X2, and the second refrigerant hole X17 communicates with the second communication hole XV2 of the valve casing X2. The hydraulic diameters of the first refrigerant holes X16 and the second refrigerant holes X17 are, for example, 0.1 mm or more and 3 mm or less, but are not limited thereto. The first refrigerant hole X16 and the second refrigerant hole X17 correspond to the first fluid hole and the second fluid hole, respectively.

The intermediate layer X12 is a conductive semiconductor member, and is sandwiched between the first outer layer X11 and the second outer layer X13. Since the intermediate layer X12 comes into contact with the oxide film of the first outer layer X11 and the oxide film of the second outer layer X13, both the first outer layer X11 and the second outer layer X13 are electrically non-conducting. As shown in FIG. 7, the intermediate layer X12 has a first fixed portion X121, a second fixed portion X122, a plurality of first ribs X123, a plurality of second ribs X124, a spine X125, an arm X126, a beam X127, and a movable layer. It has a part X128.

The first fixing portion X121 is a member fixed to the first outer layer X11 and the second outer layer X13. The first fixed portion X121 is formed so as to surround the second fixed portion X122, the first rib X123, the second rib X124, the spine X125, the arm X126, the beam X127, and the movable portion X128 in the same fluid chamber X19. There is. The fluid chamber X19 is a chamber surrounded by a first fixing portion X121, a first outer layer X11, and a second outer layer X13. At least a part of the refrigerant that has passed through the radiator 12 flows through the fluid chamber X19. The first fixed portion X121, the first outer layer X11, and the second outer layer X13 correspond to the base portion as a whole. The electrical wirings X6 and X7 are electrical wirings for changing the temperature of the plurality of first ribs X123 and the plurality of second ribs X124 to displace them.

Fixing the first fixing portion X121 to the first outer layer X11 and the second outer layer X13 suppresses the refrigerant from leaking from the fluid chamber X19 through the other than the first refrigerant hole X16 and the second refrigerant hole X17. It is done in the form of

The second fixing portion X122 is fixed to the first outer layer X11 and the second outer layer X13. The second fixed portion X122 is surrounded by the first fixed portion X121 and is arranged away from the first fixed portion X121.

The plurality of first ribs X123, the plurality of second ribs X124, the spine X125, the arm X126, the beam X127, and the movable portion X128 are not fixed to the first outer layer X11 and the second outer layer X13, and are the first. It is displaceable with respect to the outer layer X11 and the second outer layer X13.

The spine X125 has an elongated rod shape extending in the lateral direction in the rectangular shape of the intermediate layer X12. One end of the spine X125 in the longitudinal direction is connected to the beam X127.

The plurality of first ribs X123 are arranged on one side of the spine X125 in a direction orthogonal to the longitudinal direction of the spine X125. The plurality of first ribs X123 are arranged in the longitudinal direction of the spine X125. Each first rib X123 has an elongated rod shape and can be expanded and contracted according to temperature.

Each first rib X123 is connected to the first fixing portion X121 at one end in the longitudinal direction thereof and to the spine X125 at the other end. Each of the first ribs X123 is skewed with respect to the spine X125 so that the closer the first rib X123 is from the first fixed portion X121 side to the spine X125 side, the more it is offset toward the beam X127 side in the longitudinal direction of the spine X125. .. The plurality of first ribs X123 extend parallel to each other.

The plurality of second ribs X124 are arranged on the other side of the spine X125 in a direction orthogonal to the longitudinal direction of the spine X125. The plurality of second ribs X124 are arranged in the longitudinal direction of the spine X125. Each second rib X124 has an elongated rod shape and can be expanded and contracted according to temperature.

Each second rib X124 is connected to the second fixing portion X122 at one end in the longitudinal direction thereof and to the spine X125 at the other end. Each of the second ribs X124 is skewed with respect to the spine X125 so as to approach the spine X125 side from the second fixed portion X122 side so that the second rib X124 is offset toward the beam X127 side in the longitudinal direction of the spine X125. .. The plurality of second ribs X124 extend in parallel with each other. The plurality of first ribs X123, the plurality of second ribs X124, and the spine X125 correspond to the drive unit as a whole.

The arm X126 has an elongated rod shape extending non-orthogonally and parallel to the spine X125. One end of the arm X126 in the longitudinal direction is connected to the beam X127, and the other end is connected to the first fixing portion X121.

The beam X127 has an elongated rod shape extending in a direction intersecting the spine X125 and the arm X126 at about 90 °. One end of the beam X127 is connected to the movable portion X128. The arm X126 and the beam X127 correspond to the amplification unit as a whole.

The connection position XP1 of the arm X126 and the beam X127, the connection position XP2 of the spine X125 and the beam X127, and the connection position XP3 of the beam X127 and the movable portion X128 are arranged in this order along the longitudinal direction of the beam X127. Then, assuming that the connection point between the first fixed portion X121 and the arm X126 is the hinge XP0, the connection position from the hinge XP0 is more than the linear distance from the hinge XP0 to the connection position XP2 in the plane parallel to the plate surface of the intermediate layer X12. The straight line distance to XP3 is longer.

The movable portion X128 adjusts the pressure of the refrigerant in the fluid chamber X19. The movable portion X128 has a rectangular shape whose outer shape extends in a direction of approximately 90 ° with respect to the longitudinal direction of the beam X127. The movable portion X128 can move integrally with the beam X127 in the fluid chamber X19. Then, by moving in this way, the movable portion X128 communicates the first refrigerant hole X16 and the second refrigerant hole X17 via the fluid chamber X19 when it is in a certain position, and is the first when it is in another position. The refrigerant hole X16 and the second refrigerant hole X17 are shut off in the fluid chamber X19. The movable portion X128 has a frame shape surrounding a through hole X120 penetrating the front and back of the intermediate layer X12. Therefore, the through hole X120 also moves integrally with the movable portion X128. The through hole X120 is a part of the fluid chamber X19.

Further, at the first application point X129 in the vicinity of the portion of the first fixed portion X121 connected to the plurality of first ribs X123, the electrical wiring X6 passing through the through hole X14 of the first outer layer X11 shown in FIG. The microvalve X1 side end of is connected. Further, the microvalve X1 side end of the electric wiring X7 passing through the through hole X15 of the first outer layer X11 shown in FIG. 5 is connected to the second application point X130 of the second fixing portion X122.

[Operation of valve module X0]
Here, the operation of the valve module X0 will be described. When the micro valve X1 is energized, a voltage is applied between the electrical wirings X6 and X7 to the first application point X129 and the second application point X130. Then, a current flows through the plurality of first ribs X123 and the plurality of second ribs X124. Due to this electric current, the plurality of first ribs X123 and the plurality of second ribs X124 generate heat and their temperatures rise. As a result, each of the plurality of first ribs X123 and the plurality of second ribs X124 expands in the longitudinal direction thereof.

As a result of such thermal expansion accompanied by a temperature rise, the plurality of first ribs X123 and the plurality of second ribs X124 urge the spine X125 toward the connection position XP2. The urged spine X125 pushes the beam X127 at the connection position XP2. In this way, the connection position XP2 corresponds to the urging position.

Then, the member composed of the beam X127 and the arm X126 integrally changes its posture with the hinge XP0 as a fulcrum and the connection position XP2 as a force point. As a result, the movable portion X128 connected to the end of the beam X127 opposite to the arm X126 also moves in the longitudinal direction to the side where the spine X125 pushes the beam X127. As a result of the movement, the movable portion X128 reaches a position where the tip in the moving direction abuts on the first fixed portion X121 as shown in FIGS. 9 and 10. Hereinafter, this position of the movable portion X128 is referred to as an energized position.

As described above, the beam X127 and the arm X126 function as a lever having the hinge XP0 as a fulcrum, the connection position XP2 as a force point, and the connection position XP3 as an action point. As described above, the linear distance from the hinge XP0 to the connection position XP3 is longer than the linear distance from the hinge XP0 to the connection position XP2 in the plane parallel to the plate surface of the intermediate layer X12. Therefore, the amount of movement of the connection position XP3, which is the point of action, is larger than the amount of movement of the connection position XP2, which is the point of effort. Therefore, the amount of displacement due to thermal expansion is amplified by the lever and transmitted to the movable portion X128.

As shown in FIGS. 9 and 10, when the movable portion X128 is in the energized position, the through hole X120 overlaps with the first refrigerant hole X16 and the second refrigerant hole X17 in the direction orthogonal to the plate surface of the intermediate layer X12. In that case, the first refrigerant hole X16 and the second refrigerant hole X17 communicate with each other through the through hole X120 which is a part of the fluid chamber X19. As a result, the refrigerant can flow between the first communication hole XV1 and the second communication hole XV2 through the first refrigerant hole X16, the through hole X120, and the second refrigerant hole X17. That is, the micro valve X1 opens. As described above, the first refrigerant hole X16, the through hole X120, and the second refrigerant hole X17 are the refrigerant flow paths through which the refrigerant flows in the micro valve X1 when the micro valve X1 is opened.

At this time, the flow path of the refrigerant in the micro valve X1 has a U-turn structure. Specifically, the refrigerant flows into the micro valve X1 from one side surface of the micro valve X1, passes through the micro valve X1, and flows out of the micro valve X1 from the same side surface of the micro valve X1. Similarly, the flow path of the refrigerant in the valve module X0 also has a U-turn structure. Specifically, the refrigerant flows into the valve module X0 from one surface of the valve module X0, passes through the valve module X0, and flows out of the valve module X0 from the same side surface of the valve module X0. The direction orthogonal to the plate surface of the intermediate layer X12 is the stacking direction of the first outer layer X11, the intermediate layer X12, and the second outer layer X13.

Further, when the micro valve X1 is not energized, the voltage application from the electric wirings X6 and X7 to the first application point X129 and the second application point X130 is stopped. Then, the current stops flowing through the plurality of first ribs X123 and the plurality of second ribs X124, and the temperatures of the plurality of first ribs X123 and the plurality of second ribs X124 decrease. As a result, each of the plurality of first ribs X123 and the plurality of second ribs X124 contracts in the longitudinal direction thereof.

As a result of such thermal contraction accompanied by a temperature drop, the plurality of first ribs X123 and the plurality of second ribs X124 urge the spine X125 to the side opposite to the connection position XP2. The urged spine X125 pulls the beam X127 at the connection position XP2. As a result, the member including the beam X127 and the arm X126 integrally changes its posture with the hinge XP0 as a fulcrum and the connection position XP2 as a force point. As a result, the movable portion X128 connected to the end of the beam X127 opposite to the arm X126 also moves in the longitudinal direction to the side where the spine X125 pulls the beam X127. As a result of the movement, the movable portion X128 reaches a position where it does not abut on the first fixed portion X121 as shown in FIGS. 7 and 8. Hereinafter, this position of the movable portion X128 is referred to as a non-energized position.

As shown in FIGS. 7 and 8, when the movable portion X128 is in the non-energized position, the through hole X120 overlaps with the first refrigerant hole X16 in the direction orthogonal to the plate surface of the intermediate layer X12, but in that direction. It does not overlap with the second refrigerant hole X17. The second refrigerant hole X17 overlaps the movable portion X128 in the direction orthogonal to the plate surface of the intermediate layer X12. That is, the second refrigerant hole X17 is closed by the movable portion X128. Therefore, in this case, the first refrigerant hole X16 and the second refrigerant hole X17 are blocked in the fluid chamber X19. As a result, the flow of the refrigerant between the first communication hole XV1 and the second communication hole XV2 through the first refrigerant hole X16 and the second refrigerant hole X17 is hindered. That is, the micro valve X1 is closed.

The flow path area of the first battery decompression unit 16 configured in this way becomes the flow path area of the orifice 273 when the micro valve X1 is not energized, and the valve module X0 is added to the flow path cross-sectional area of the orifice 273 when the micro valve X1 is energized. The size is the sum of the flow path area of. That is, as shown in FIG. 11, the pressure reducing unit 16 for the first battery has a small opening opening S1 when the microvalve X1 is not energized, and a large opening degree S2 when the microvalve X1 is energized. As described above, the decompression unit 16 for the first battery can adjust the throttle opening degree of the decompression unit 16 for the first battery by switching between energization and de-energization of the micro valve X1. Specifically, the decompression unit 16 for the first battery can reduce the throttle opening degree by stopping the energization of the micro valve X1. The cooling pressure reducing unit 14 and the second battery decompression unit 18 are configured in the same manner as the first battery decompression unit 16. Therefore, the cooling decompression unit 14 and the second battery decompression unit 18 switch between energization and de-energization of the micro valve X1 provided in each of the cooling decompression unit 14 and the second battery decompression unit 18. It is possible to adjust the throttle opening of.

In the control device 100 of the present embodiment, for example, when it is necessary to prioritize the cooling of the battery BT over the cooling of the vehicle interior, the refrigerant flow rates of the first battery evaporator 17 and the second battery evaporator 19 are large. The pressure reducing units 14, 16 and 18 are controlled so as to be. Specifically, when it is necessary to prioritize the cooling of the battery BT over the cooling of the vehicle interior, the control device 100 energizes the microvalves X1 of the decompression unit 16 for the first battery and the decompression unit 18 for the second battery. Then, the energization of the cooling pressure reducing unit 14 to the micro valve X1 is stopped. According to this, since the battery cooling capacity of the refrigeration cycle device 10 is increased, the cooling of the battery BT can be prioritized over the cooling of the vehicle interior.

Further, when it is necessary to prioritize the cooling of the vehicle interior over the cooling of the battery BT, the control device 100 sets the decompression units 14, 16 and 18 so that the refrigerant flow rate of the cooling evaporator 15 becomes large. Control. Specifically, when the control device 100 needs to prioritize the cooling of the vehicle interior over the cooling of the battery BT, the control device 100 energizes the micro valve X1 of the cooling decompression unit 14, and the first battery decompression unit 16 and the first battery decompression unit 16 and the first. 2 The energization of the micro valve X1 of each of the battery decompression units 18 is stopped. According to this, since the cooling capacity of the refrigerating cycle device 10 is increased, the cooling of the vehicle interior can be prioritized over the cooling of the battery BT.

The refrigeration cycle apparatus 10 described above corresponds to the cooling evaporator 15, the first battery evaporator 17, and the second battery evaporator 19 which are connected in parallel with each other, and corresponds to the cooling decompression unit 14, the first. A battery decompression unit 16 and a second battery decompression unit 18 are provided. As a result, the refrigerant and the refrigerating machine oil can be distributed to the evaporators 15, 17, and 19 in a desired ratio.

In addition, since the pressure reducing portions 14, 16 and 18 are configured to adjust the throttle opening degree by using the micro valve X1, the size can be easily reduced as compared with the case where the solenoid valve and the electric valve are used. One of the reasons is that the microvalve X1 is formed of a semiconductor chip as described above. Further, as described above, the fact that the displacement amount due to thermal expansion is amplified by using a lever also contributes to miniaturization as compared with a solenoid valve or an electric valve that does not use such a lever.

Therefore, according to the refrigerating cycle apparatus 10 of the present embodiment, the refrigerant and the refrigerating machine oil are distributed in a desired ratio to the evaporators 15, 17, and 19 connected in parallel while suppressing the deterioration of the mountability. be able to.

Further, since the lever is used, the amount of displacement due to thermal expansion can be suppressed from the amount of movement of the movable portion X128. Therefore, the power consumption for driving the movable portion X128 can also be reduced. Further, since the impact noise when the solenoid valve is driven can be eliminated, the noise can be reduced. Further, since the displacement of the plurality of first ribs X123 and the plurality of second ribs X124 is generated due to heat, the noise reduction effect is high.

Further, each of the pressure reducing portions 14, 16 and 18 includes an orifice 273 having a fixed throttle opening degree. The microvalve X1 is configured to adjust the throttle opening degrees of the decompression portions 14, 16 and 18 by switching the communication and interruption of the first refrigerant hole X16 and the second refrigerant hole X17 by the movable portion X128. ..

In this way, if each of the decompression units 14, 16 and 18 is configured to include a fixed throttle, each of the decompression units 14 can be switched between communication and interruption of the first refrigerant hole X16 and the second refrigerant hole X17 in the micro valve X1. , 16 and 18 can be adjusted in stages. Further, when each of the decompression units 14, 16 and 18 includes a fixed throttle, the micro valve X1 is not driven when it is not necessary to adjust the throttle opening of each of the decompression units 14, 16 and 18. The drive frequency of X1 can be reduced to reduce energy consumption.

As described above, the valve casing X2 is made of a resin material in which the coefficient of linear expansion of the valve casing X2 is a value between the coefficient of linear expansion of the microvalve X1 and the coefficient of linear expansion of the block body 27. As a result, the valve casing X2 can absorb the difference in the coefficient of linear expansion between the micro valve X1 and the block body 27. That is, since the stress of thermal strain due to the temperature change of the block body 27 is absorbed by the valve casing X2, the micro valve X1 can be protected.

Further, since both the micro valve X1 and the valve module X0 have a refrigerant flow path having a U-turn structure, it is possible to reduce the digging of the block body 27. That is, the depth of the recess formed in the block body 27 for arranging the valve module X0 can be suppressed. The reason is as follows.

For example, the valve module X0 does not have a refrigerant flow path having a U-turn structure, the valve module X0 has a refrigerant inlet on the block 27 side surface, and the valve module X0 has a refrigerant outlet on the opposite surface. Suppose. In that case, it is necessary to form refrigerant flow paths on both sides of the valve module X0. Therefore, if the block body 27 tries to accommodate the refrigerant flow paths on both sides of the valve module X0, the dent that must be formed in the block body 27 in order to arrange the valve module X0 becomes deep. Further, since the micro valve X1 itself is small, the digging of the block body 27 can be further reduced.

Further, when the electrical wirings X6 and X7 are arranged on the surface of both sides of the microvalve X1 opposite to the surface on which the first refrigerant holes X16 and the second refrigerant holes X17 are formed, the electrical wirings X6 and X7 are placed in the atmosphere. Can be placed closer to the atmosphere. Therefore, a seal structure such as a hermetic for reducing the influence of the refrigerant atmosphere on the electric wirings X6 and X7 becomes unnecessary. As a result, the decompression portions 14, 16 and 18 can be downsized.

Further, since the micro valve X1 is lightweight, the pressure reducing portions 14, 16 and 18 are reduced in weight. Since the power consumption of the micro valve X1 is small, the power saving units 14, 16 and 18 are reduced.

(Second Embodiment)
Next, the second embodiment will be described with reference to FIG. The present embodiment is different from the first embodiment in that the pressure regulating valve 20A is arranged on the downstream side of the refrigerant flow of the cooling evaporator 15. In the present embodiment, the parts different from the first embodiment will be mainly described, and the same parts as those in the first embodiment may be omitted.

As shown in FIG. 12, in the refrigeration cycle device 10, a pressure regulating valve 20A is arranged between the cooling evaporator 15 and the second confluence portion 24. The pressure regulating valve 20A maintains the pressure of the refrigerant passing through the cooling evaporator 15 at a predetermined set pressure value or higher.

Other configurations are the same as those in the first embodiment. The refrigeration cycle device 10 of the present embodiment has the same configuration as that of the first embodiment, and can obtain the action and effect produced from the common configuration as in the first embodiment.

In particular, the refrigeration cycle device 10 of the present embodiment is provided with a pressure regulating valve 20A on the downstream side of the refrigerant flow of the cooling evaporator 15. Therefore, for example, when cooling the battery BT and cooling the passenger compartment at the same time, the pressure of the refrigerant passing through the evaporators 17 and 19 for each battery is maintained while maintaining the pressure of the refrigerant passing through the evaporator 15 for cooling. Can be lowered.

(Third Embodiment)
Next, the third embodiment will be described with reference to FIGS. 13 and 14. The present embodiment is different from the first embodiment in that the orifice 273 is not provided for the block body 27A. In the present embodiment, the parts different from the first embodiment will be mainly described, and the same parts as those in the first embodiment may be omitted.

As shown in FIG. 13, the block body 27A is not provided with an orifice 273 between the upstream fitting hole 271 and the downstream fitting hole 272. That is, in the block body 27A, a partition portion 276 is set between the bottom surfaces of the fitting holes 271 and 272 so that the refrigerant does not flow directly from the upstream fitting hole 271 to the downstream fitting hole 272. ing.

Here, the microvalve X1 is a movable portion with respect to the non-energized position as the power supplied from the electrical wirings X6 and X7 to the microvalve X1 via the first application point X129 and the second application point X130 when energized is larger. The amount of movement of X128 also increases. This is because the higher the electric power supplied to the micro valve X1, the higher the temperature of the first rib X123 and the second rib X124, and the greater the degree of expansion. For example, when the voltage applied from the electrical wirings X6 and X7 to the first application point X129 and the second application point X130 is PWM controlled, the larger the duty ratio, the larger the amount of movement of the movable portion X128 with respect to the non-energized state.

Therefore, the micro valve X1 can stop the movable portion X128 at any intermediate position between the non-energized position and the maximum energized position by adjusting the electric power supplied to the micro valve X1. ..

For example, in order to stop the movable portion X128 at a position equidistant from the maximum energized position and the non-energized position (that is, the central position), the power supplied to the micro valve X1 is the maximum value within the control range. It should be half. For example, the duty ratio of PWM control may be 50%.

When the movable portion X128 is stopped at an intermediate position, both the first refrigerant hole X16 and the second refrigerant hole X17 communicate with the through hole X120. However, the second refrigerant hole X17 is not fully open with respect to the through hole Y120, and has an opening degree of less than 100% and larger than 0%. As the movable portion X128 approaches the position at the maximum potential at the intermediate position, the opening degree of the second refrigerant hole X17 with respect to the through hole X120 increases.

In consideration of these factors, in the refrigeration cycle device 10 of the present embodiment, the throttle opening degrees of the decompression units 14, 16 and 18 are changed by changing the voltage applied to the micro valve X1 by PWM control. For example, as shown in FIG. 14, the refrigeration cycle apparatus 10 increases the throttle opening of each of the decompression units 14, 16 and 18 by increasing the duty ratio of PWM control, and decreases the duty ratio of PWM control. The throttle opening of each of the decompression portions 14, 16 and 18 is reduced.

For example, when it is necessary to prioritize the cooling of the battery BT over the cooling of the vehicle interior, the control device 100 increases the duty ratio of the PWM control to the microvalves X1 of the decompression units 16 and 18 for each battery. Then, the control device 100 reduces the duty ratio of the PWM control to the micro valve X1 of the cooling pressure reducing unit 14. According to this, since the battery cooling capacity of the refrigeration cycle device 10 is increased, the cooling of the battery BT can be prioritized over the cooling of the vehicle interior.

Further, when it is necessary to prioritize the cooling of the vehicle interior over the cooling of the battery BT, the control device 100 increases the duty ratio of the PWM control to the micro valve X1 of the cooling pressure reducing unit 14. Then, the control device 100 reduces the duty ratio of the PWM control to the microvalves X1 of the decompression units 16 and 18 for each battery. According to this, since the cooling capacity of the refrigerating cycle device 10 is increased, the cooling of the vehicle interior can be prioritized over the cooling of the battery BT.

Other configurations and operations are the same as in the first embodiment. Each of the decompression units 14, 16 and 18 of the present embodiment can adjust the throttle opening degree of each of the decompression units 14, 16 and 18 by adjusting the electric power supplied to the micro valve X1. Specifically, each of the decompression units 14, 16 and 18 changes the refrigerant flow rate to a large flow rate by increasing the duty ratio of the PWM control, and reduces the duty ratio of the PWM control to reduce the refrigerant flow rate. It is possible to change to.

In this way, if the micro valve X1 is configured as a variable throttle in which the throttle opening of each of the decompression portions 14, 16 and 18 can be changed, the opening of the fluid hole in the micro valve X1 can be changed to change the opening of each decompression portion 14. , 16 and 18 can be adjusted to a desired opening degree. According to this, even if the block body 27A is not provided with a fixed throttle such as an orifice 273, the refrigerant can be distributed to the evaporators 15, 17, and 19 at a desired ratio. The action and effect obtained by each of the decompression portions 14, 16 and 18 including the micro valve X1 can be obtained in the same manner as in the first embodiment.

(Modified example of the third embodiment)
In the third embodiment described above, an example in which the orifice 273 is not provided in the block body 27A of each of the decompression portions 14, 16 and 18 has been described, but the present invention is not limited thereto. Each of the decompression portions 14, 16 and 18 may be provided with an orifice 273 with respect to the block body 27A.

(Fourth Embodiment)
Next, the fourth embodiment will be described with reference to FIGS. 15 and 16. The present embodiment is different from the third embodiment in that the decompression unit 16 for the first battery is integrally configured with the evaporator 17 for the first battery. In the present embodiment, the parts different from the third embodiment will be mainly described, and the same parts as those in the third embodiment may be omitted.

As shown in FIG. 15, the decompression unit 16 for the first battery is integrally configured with the refrigerant inlet portion 170 of the evaporator 17 for the first battery. Specifically, the decompression unit 16 for the first battery also functions as a connector for connecting the refrigerant inlet portion 170 of the evaporator 17 for the first battery and the refrigerant pipe 26.

As shown in FIG. 16, the block body 27C of the decompression unit 16 for the first battery is a metal (for example, aluminum) joint that connects the refrigerant pipe 26 and the refrigerant inlet portion 170 of the evaporator 17 for the first battery. is there.

A bottomed upstream fitting hole 271 into which the refrigerant pipe 26 is fitted is formed on the side surface of the block body 27C. Further, the block body 27C has a bottomed downstream fitting hole 272 in which the refrigerant inlet portion 170 of the first battery evaporator 17 is fitted on the upper surface connected to the side surface on which the upstream fitting hole 271 is formed. It is formed. The upstream fitting hole 271 and the downstream fitting hole 272 are partitioned by a partition portion 276 set between the fitting holes 271 and 272.

Here, the downstream fitting hole 272 extends in a direction orthogonal to the extending direction of the upstream fitting hole 271. Specifically, the downstream fitting hole 272 is formed so as to extend along the projecting direction of the refrigerant inlet portion 170 so that the refrigerant travels straight to the refrigerant inlet portion 170.

Other configurations are the same as those in the fourth embodiment. Since the refrigeration cycle device 10 of the present embodiment has the same components as those of the fourth embodiment, it is possible to obtain the same effects as those of the fourth embodiment.

In particular, the refrigeration cycle device 10 of the present embodiment is fitted so that the block body 27C of the decompression unit 16 for the first battery and the refrigerant inlet portion 170 of the evaporator 17 for the first battery are integrated. As described above, if the decompression unit 16 for the first battery is configured at the connection portion between the refrigerant pipe 26 and the refrigerant inlet portion 170 of the evaporator 17 for the first battery, the refrigeration cycle device 10 can be simplified.

Further, a high-temperature and high-pressure refrigerant before passing through the first battery decompression unit 16 flows through the refrigerant pipe 26. In such a configuration, when the refrigerant flows through the refrigerant pipe 26, heat can be dissipated around the refrigerant pipe 26, so that the heat absorption capacity of the first battery evaporator 17 can be improved. Such a configuration is suitable when the evaporator 17 for the first battery is used as a heat exchanger on the user side.

(Modified example of the fourth embodiment)
In the above-described fourth embodiment, the decompression unit 16 for the first battery is integrally configured with the evaporator 17 for the first battery, but the present invention is not limited to this. In the refrigeration cycle device 10, for example, the cooling decompression unit 14 is integrally configured with the cooling evaporator 15, and the second battery decompression unit 18 is integrated with the second battery evaporator 19. It may be configured in.

In the above-described fourth embodiment, examples of the block body 27C in which the fitting holes 271 and 272 extend in directions orthogonal to each other are illustrated, but the present invention is not limited thereto. The decompression portions 14, 16 and 18 may be formed so that the fitting holes 271 and 272 extend in the same direction with respect to the block body 27C, for example. Further, an orifice 273 may be formed with respect to the block body 27C.

(Fifth Embodiment)
Next, the fifth embodiment will be described with reference to FIGS. 17 to 26. The present embodiment is different from the first embodiment in that the throttle openings of the depressurizing portions 14, 16 and 18 are changed by utilizing the pressure difference of the refrigerant. In the present embodiment, the parts different from the first embodiment will be mainly described, and the same parts as those in the first embodiment may be omitted.

Each of the decompression units 14, 16 and 18 is configured to drive the main valve body 285 for adjusting the throttle opening degree by the valve module Y0. The valve module Y0 constitutes a driving member that drives the main valve body 285.

Since the decompression units 14, 16 and 18 are configured in the same manner, the configuration of the decompression unit 16 for the first battery will be described below, and the decompression unit 14 for cooling and the decompression unit 18 for the second battery will be described. Omit.

As shown in FIGS. 17 and 18, the valve module Y0 is integrally configured with respect to the block body 28 provided in the refrigerant pipe 26 connecting the second branch portion 22 and the first battery evaporator 17. ing. The block body 28 constitutes an object to be attached to be attached to the micro valve Y1.

The block body 28 constitutes a part of the decompression unit 16 for the first battery. The block body 28 is made of metal that connects the upstream portion 261 connected to the second branch portion 22 of the refrigerant pipe 26 and the downstream portion 262 connected to the refrigerant inlet portion 170 of the first battery evaporator 17 ( For example, aluminum) joints.

A bottomed upstream fitting hole 281 into which the upstream portion 261 is fitted is formed on one side surface of the block body 28. The upstream fitting hole 281 constitutes an inlet flow path through which the refrigerant from the radiator 12 flows.

Further, the block body 28 is formed with a bottomed downstream fitting hole 282 into which the downstream side portion 262 is fitted on the opposite side of one side surface on which the upstream fitting hole 281 is formed. The downstream fitting hole 282 constitutes an outlet flow path through which the refrigerant flows out toward the first battery evaporator 17.

A valve chamber 283 in which the main valve body 285 is housed is formed between the upstream fitting hole 281 and the downstream fitting hole 282. The valve chamber 283 extends in a direction orthogonal to the arrangement direction of the upstream fitting hole 281 and the downstream fitting hole 282. The valve chamber 283 communicates with the upstream fitting hole 281 via the first through hole 281a and communicates with the downstream fitting hole 282 via the second through hole 282a. The second through hole 282a forms a throttle flow path 284 whose throttle opening degree is adjusted by the main valve body 285.

In the valve chamber 283, a main valve body 285 for adjusting the throttle opening degree of the throttle flow path 284 is slidably housed. The main valve body 285 is arranged in the valve chamber 283 so as to be slidable along the extending direction of the valve chamber 283. The main valve body 285 has a curved surface whose tip portion located on the throttle flow path 284 side is curved hemispherically.

The valve chamber 283 is divided by the main valve body 285 into a space on the throttle flow path 284 side through which the refrigerant flows and an opening degree adjusting chamber 286 for adjusting the throttle opening degree of the throttle flow path 284. The opening degree adjusting chamber 286 is a space in the valve chamber 283 that is opposite to the throttle flow path 284 with the main valve body 285 interposed therebetween. In the opening degree adjusting chamber 286, a refrigerant for pressing the main valve body 285 toward the valve opening side or the valve closing side is introduced by the micro valve Y1 described later.

A spring 286a is arranged in the opening degree adjusting chamber 286. The spring 286a is a cylindrical coil spring extending in the displacement direction of the main valve body 285. The spring 286a is an elastic member for applying a load for urging the main valve body 285 in the valve closing direction.

Further, on the lower surface of the block body 28, a first recess 287, a second recess 288, and a third recess into which the first protrusion Y21, the second protrusion Y22, and the third protrusion Y23 of the valve module Y0, which will be described later, are fitted. 289 is formed. The first recess 287, the second recess 288, and the third recess 289 are arranged so as to be linearly arranged in the order of the second recess 288, the first recess 287, and the third recess 289 when the lower surface of the block body 28 is viewed. Has been done. The first recess 287 is connected to the valve chamber 283 and communicates with the opening degree adjusting chamber 286. At the bottom of the second recess 288, a through hole 288a is formed to communicate the second recess 288 and the upstream fitting hole 271. At the bottom of the third recess 289, a through hole 289a is formed to communicate the third recess 289 and the downstream fitting hole 282.

In the first battery decompression unit 16 configured in this way, the flow path area (that is, the throttle opening degree) of the throttle flow path 284 changes depending on the position of the main valve body 285. The main valve body 285 is determined by the force acting on the main valve body 285. Specifically, the balance of the load acting on the main valve body 285 can be expressed by the following mathematical formula F1.

Ph × As = Ks × L + F0 + Pm × As… (F1)
Here, in the above-mentioned formula F1, the refrigerant pressure (that is, high pressure) that has passed through the radiator 12 is indicated by Ph, and the refrigerant pressure (that is, control pressure) of the opening degree adjusting chamber 286 is indicated by Pm, and the main valve body. The pressure receiving area of 285 is indicated by As. Further, in the above equation F1, the spring constant of the spring 286a is indicated by Ks, the displacement amount of the main valve body 285 is indicated by L, and the initial load of the spring 286a acting on the main valve body 285 is indicated by F0. ..

When the control pressure Pm of the first battery decompression unit 16 is equal to the refrigerant pressure on the downstream side of the throttle flow path 284 (that is, the low pressure pressure Pl), the pressure difference between the high pressure pressure Ph and the control pressure Pm is large. As shown in FIG. 17, the main valve body 285 is displaced to the position where the throttle opening is maximized.

When the control pressure Pm becomes higher than the low pressure pressure Pl from this state, the pressure difference between the high pressure pressure Ph and the control pressure Pm becomes small, so that the main valve body 285 is displaced to a position where the throttle opening becomes small. Then, when the control pressure Pm becomes a pressure equivalent to the high pressure pressure Ph, the main valve body 285 is urged in the valve closing direction by the spring 286a, so that the main valve body 285 has a throttle opening degree as shown in FIG. Is displaced to the maximum position.

Therefore, as shown in FIG. 19, the pressure reducing unit 16 for the first battery has a throttle opening which is a flow path area of the throttle flow path 284 when the control pressure Pm becomes small, and a throttle when the control pressure Pm becomes large. The structure is such that the opening is small.

In the first battery decompression unit 16 of the present embodiment, the control pressure Pm is adjusted by the micro valve Y1 provided in the valve module Y0. The details of the valve module Y0 will be described below.

[Valve module Y0 configuration]
As shown in FIGS. 17 and 18, the valve module Y0 includes a micro valve Y1, a valve casing Y2, a sealing member Y3, three O-rings Y4, Y5a, Y5b, two electrical wirings Y6, Y7, and a conversion plate Y8. have.

The micro valve Y1 is a plate-shaped valve component, and is mainly composed of a semiconductor chip. The microvalve Y1 may or may not have a component other than the semiconductor chip. Therefore, the micro valve Y1 can be made compact. The micro valve Y1 is a valve component for adjusting the pressure of the refrigerant in the opening degree adjusting chamber 286.

The length of the microvalve Y1 in the thickness direction is, for example, 2 mm, the length in the longitudinal direction orthogonal to the thickness direction is, for example, 10 mm, and the length in the lateral direction orthogonal to both the longitudinal direction and the thickness direction. Is, for example, 5 mm, but is not limited thereto. As the power supplied to the micro valve Y1 fluctuates, the flow path configuration of the micro valve Y1 changes. The micro valve Y1 functions as a pilot valve for driving the main valve body 285.

The electrical wirings Y6 and Y7 extend from the surface of the two plate surfaces of the microvalve Y1 opposite to the valve casing Y2, pass through the sealing member Y3 and the valve casing Y2, and pass through the outside of the valve module Y0. Connected to the power supply at. As a result, electric power is supplied from the power source to the micro valve Y1 through the electric wires Y6 and Y7.

The conversion plate Y8 is a plate-shaped member arranged between the micro valve Y1 and the valve casing Y2. The conversion plate Y8 is a glass substrate. One side of the two plate surfaces of the conversion plate Y8 is fixed to the microvalve Y1 with an adhesive, and the other side is fixed to the valve casing Y2 with an adhesive. The conversion plate Y8 is formed with flow paths Y81, Y82, and Y83 for connecting the three refrigerant holes described later of the micro valve Y1 and the three communication holes of the valve casing Y2. The flow paths Y81, Y82, and Y83 are members for absorbing the difference between the pitches of the three refrigerant holes arranged in a row and the pitches of the three communicating holes arranged in a row. The flow paths Y81, Y82, and Y83 penetrate from one of the two plate surfaces of the conversion plate Y8 to the other.

The valve casing Y2 is a resin casing that houses the microvalve Y1 and the conversion plate Y8. The valve casing Y2 is formed by resin molding containing polyphenylene sulfide as a main component. The valve casing Y2 is configured such that the coefficient of linear expansion is a value between the coefficient of linear expansion of the microvalve Y1 and the coefficient of linear expansion of the block body 28. The valve casing Y2 constitutes a component mounting portion for mounting the microvalve Y1 to the block body 28. The valve casing Y2 is a box body having a bottom wall on one side and an open side on the other side. The bottom wall of the valve casing Y2 is interposed between the block body 28 and the micro valve Y1 so that the micro valve Y1 and the conversion plate Y8 do not come into direct contact with the block body 28. Then, one surface of the bottom wall is in contact with and fixed to the block body 28, and the other surface is in contact with and fixed to the conversion plate Y8.

In this way, the valve casing Y2 can absorb the difference in the coefficient of linear expansion between the micro valve Y1 and the block body 28. This is because the coefficient of linear expansion of the valve casing Y2 is a value between the coefficient of linear expansion of the microvalve Y1 and the coefficient of linear expansion of the block body 28. The coefficient of linear expansion of the conversion plate Y8 is a value between the coefficient of linear expansion of the microvalve Y1 and the coefficient of linear expansion of the valve casing Y2. Here, the valve casing Y2 constitutes a component mounting portion for mounting the microvalve Y1 to the block body 28.

Further, the bottom wall of the valve casing Y2 has a plate-shaped base portion Y20 facing the micro valve Y1 and a pillar-shaped first protruding portion Y21 and a second protruding portion Y21 protruding from the base portion Y20 in a direction away from the micro valve Y1. It has a portion Y22 and a third protruding portion Y23.

The first protruding portion Y21, the second protruding portion Y22, and the third protruding portion Y23 are fitted into the first recess 287, the second recess 288, and the third recess 289 formed on the lower surface of the block body 28. The first protruding portion Y21 is formed with a first communication hole YV1 that penetrates from the end on the side of the micro valve Y1 to the end on the opposite side. The second protruding portion Y22 is formed with a second communication hole YV2 that penetrates from the end on the side of the microvalve Y1 to the end on the opposite side. The third protruding portion Y23 is formed with a third communication hole YV3 that penetrates from the end on the side of the micro valve Y1 to the end on the opposite side. The first communication hole YV1, the second communication hole YV2, and the third communication hole YV3 are arranged in a row, and the first communication hole YV1 is located between the second communication hole YV2 and the third communication hole YV3.

The microvalve Y1 side end of the first communication hole YV1 communicates with the valve casing Y2 side end of the flow path Y81 formed in the conversion plate Y8. The microvalve Y1 side end of the second communication hole YV2 communicates with the valve casing Y2 side end of the flow path Y82 formed in the conversion plate Y8. The microvalve Y1 side end of the third communication hole YV3 communicates with the valve casing Y2 side end of the flow path Y83 formed in the conversion plate Y8.

The sealing member Y3 is a member made of epoxy resin that seals the other open side of the valve casing Y2. The sealing member Y3 covers the entire plate surface of the two front and back surfaces of the micro valve Y1 on the side opposite to the conversion plate Y8 side. Further, the sealing member Y3 covers a part of the plate surface of the conversion plate Y8 on the side opposite to the bottom wall side of the valve casing Y2. Further, the sealing member Y3 covers the electrical wirings Y6 and Y7 to realize waterproofing and insulation of the electrical wirings Y6 and Y7. The sealing member Y3 is formed by resin potting or the like.

The O-ring Y4 is attached to the outer periphery of the first protruding portion Y21 and seals between the block body 28 and the first protruding portion Y21 to the outside of the decompression portions 14, 16 and 18 and to the outside of the refrigerant circuit. Suppress the leakage of the refrigerant. The O-ring Y5a is attached to the outer periphery of the second protruding portion Y22, and by sealing between the block body 28 and the second protruding portion Y22, to the outside of the decompression portions 14, 16 and 18 and to the outside of the refrigerant circuit. Suppress the leakage of the refrigerant. The O-ring Y5b is attached to the outer periphery of the third protruding portion Y23, and by sealing between the block body 28 and the third protruding portion Y23, to the outside of the decompression portions 14, 16 and 18 and to the outside of the refrigerant circuit. Suppress the leakage of the refrigerant.

[Structure of micro valve Y1]
Here, the configuration of the micro valve Y1 will be further described. As shown in FIGS. 20 and 21, the microvalve Y1 is a MEMS having a first outer layer Y11, an intermediate layer Y12, and a second outer layer Y13, all of which are semiconductors. The first outer layer Y11, the intermediate layer Y12, and the second outer layer Y13 are rectangular plate-shaped members having the same outer shape, and are laminated in the order of the first outer layer Y11, the intermediate layer Y12, and the second outer layer Y13. Of the first outer layer Y11, the intermediate layer Y12, and the second outer layer Y13, the second outer layer Y13 is arranged on the side closest to the bottom wall of the valve casing Y2. The structures of the first outer layer Y11, the intermediate layer Y12, and the second outer layer Y13, which will be described later, are formed by a semiconductor manufacturing process such as chemical etching.

The first outer layer Y11 is a conductive semiconductor member having a non-conductive oxide film on its surface. As shown in FIG. 20, the first outer layer Y11 is formed with two through holes Y14 and Y15 penetrating the front and back surfaces. The microvalve Y1 side ends of the electrical wirings Y6 and Y7 are inserted into the through holes Y14 and Y15, respectively.

The second outer layer Y13 is a conductive semiconductor member having a non-conductive oxide film on its surface. As shown in FIGS. 20, 22, and 23, the second outer layer Y13 is formed with a first refrigerant hole Y16, a second refrigerant hole Y17, and a third refrigerant hole Y18 penetrating the front and back surfaces. The hydraulic diameters of the first refrigerant hole Y16, the second refrigerant hole Y17, and the third refrigerant hole Y18 are, for example, 0.1 mm or more and 3 mm or less, but are not limited thereto. The first refrigerant hole Y16, the second refrigerant hole Y17, and the third refrigerant hole Y18 correspond to the first fluid hole, the second fluid hole, and the third fluid hole, respectively.

As shown in FIG. 23, the first refrigerant hole Y16, the second refrigerant hole Y17, and the third refrigerant hole Y18 communicate with the flow paths Y81, Y82, and Y83 of the conversion plate Y8, respectively. The first refrigerant hole Y16, the second refrigerant hole Y17, and the third refrigerant hole Y18 are arranged in a row. The first refrigerant hole Y16 is arranged between the second refrigerant hole Y17 and the third refrigerant hole Y18.

The intermediate layer Y12 is a conductive semiconductor member, and is sandwiched between the first outer layer Y11 and the second outer layer Y13. Since the intermediate layer Y12 comes into contact with the oxide film of the first outer layer Y11 and the oxide film of the second outer layer Y13, both the first outer layer Y11 and the second outer layer Y13 are electrically non-conducting. As shown in FIG. 22, the intermediate layer Y12 has a first fixed portion Y121, a second fixed portion Y122, a plurality of first ribs Y123, a plurality of second ribs Y124, a spine Y125, an arm Y126, a beam Y127, and a movable beam. It has a part Y128.

The first fixing portion Y121 is a member fixed to the first outer layer Y11 and the second outer layer Y13. The first fixed portion Y121 is formed so as to surround the second fixed portion Y122, the first rib Y123, the second rib Y124, the spine Y125, the arm Y126, the beam Y127, and the movable portion Y128 in the same fluid chamber Y19. There is. It is a chamber surrounded by a first fixing portion Y121, a first outer layer Y11, and a second outer layer Y13. In the fluid chamber Y19, the refrigerant introduced into the opening degree adjusting chamber 286 flows through the fluid chamber Y19. The first fixed portion Y121, the first outer layer Y11, and the second outer layer Y13 correspond to the base portion as a whole. The electrical wirings Y6 and Y7 are electrical wirings for changing the temperature of the plurality of first ribs Y123 and the plurality of second ribs Y124 to displace them.

In the fixing of the first fixing portion Y121 to the first outer layer Y11 and the second outer layer Y13, the refrigerant passes from the fluid chamber Y19 through other than the first refrigerant hole Y16, the second refrigerant hole Y17, and the third refrigerant hole Y18 from the micro valve Y1. It is performed in a form that suppresses leakage.

The second fixing portion Y122 is fixed to the first outer layer Y11 and the second outer layer Y13. The second fixed portion Y122 is surrounded by the first fixed portion Y121 and is arranged away from the first fixed portion Y121.

The plurality of first ribs Y123, the plurality of second ribs Y124, the spine Y125, the arm Y126, the beam Y127, and the movable portion Y128 are not fixed to the first outer layer Y11 and the second outer layer Y13, and are the first. It can be displaced with respect to the outer layer Y11 and the second outer layer Y13.

The spine Y125 has a rectangular shape of the intermediate layer Y12 and an elongated rod shape extending in the lateral direction. One end of the spine Y125 in the longitudinal direction is connected to the beam Y127.

The plurality of first ribs Y123 are arranged on one side of the spine Y125 in a direction orthogonal to the longitudinal direction of the spine Y125. The plurality of first ribs Y123 are arranged in the longitudinal direction of the spine Y125. Each first rib Y123 has an elongated rod shape and can be expanded and contracted according to temperature.

Each first rib Y123 is connected to the first fixing portion Y121 at one end in the longitudinal direction thereof and to the spine Y125 at the other end. Each of the first ribs Y123 is oblique with respect to the spine Y125 so as to approach the spine Y125 side from the first fixed portion Y121 side so as to be offset toward the beam Y127 side in the longitudinal direction of the spine Y125. .. The plurality of first ribs Y123 extend in parallel with each other.

The plurality of second ribs Y124 are arranged on the other side of the spine Y125 in a direction orthogonal to the longitudinal direction of the spine Y125. The plurality of second ribs Y124 are arranged in the longitudinal direction of the spine Y125. Each second rib Y124 has an elongated rod shape and can be expanded and contracted according to the temperature.

Each second rib Y124 is connected to the second fixing portion Y122 at one end in the longitudinal direction thereof and to the spine Y125 at the other end. Each of the second ribs Y124 is skewed with respect to the spine Y125 so as to approach the spine Y125 side from the second fixed portion Y122 side so as to be offset toward the beam Y127 side in the longitudinal direction of the spine Y125. .. The plurality of second ribs Y124 extend in parallel with each other.

The plurality of first ribs Y123, the plurality of second ribs Y124, and the spine Y125 correspond to the drive unit as a whole.

The arm Y126 has an elongated rod shape extending non-orthogonally and parallel to the spine Y125. One end of the arm Y126 in the longitudinal direction is connected to the beam Y127, and the other end is connected to the first fixing portion Y121.

The beam Y127 has an elongated rod shape extending in a direction intersecting the spine Y125 and the arm Y126 at about 90 °. One end of the beam Y127 is connected to the movable portion Y128. The arm Y126 and the beam Y127 correspond to the amplification unit as a whole.

The connection position YP1 between the arm Y126 and the beam Y127, the connection position YP2 between the spine Y125 and the beam Y127, and the connection position YP3 between the beam Y127 and the movable portion Y128 are arranged in this order along the longitudinal direction of the beam Y127. If the connection point between the first fixing portion Y121 and the arm Y126 is a hinge YP0, the connection position from the hinge YP0 is more than the linear distance from the hinge YP0 to the connection position YP2 in the plane parallel to the plate surface of the intermediate layer Y12. The straight line distance to YP3 is longer. For example, the value obtained by dividing the former linear distance by the latter linear distance may be 1/5 or less, or may be 1/10 or less.

The movable portion Y128 adjusts the pressure of the refrigerant flowing through the fluid chamber Y19. The movable portion Y128 has a rectangular shape whose outer shape extends in a direction of approximately 90 ° with respect to the longitudinal direction of the beam Y127. The movable portion Y128 can move integrally with the beam Y127 in the fluid chamber Y19. The movable portion Y128 has a frame shape surrounding the through hole Y120 penetrating the front and back of the intermediate layer Y12. Therefore, the through hole Y120 also moves integrally with the movable portion Y128. The through hole Y120 is a part of the fluid chamber Y19.

By moving as described above, the movable portion Y128 changes the opening degree of the second refrigerant hole Y17 with respect to the through hole Y120 and the opening degree of the third refrigerant hole Y18 with respect to the through hole Y120. The first refrigerant hole Y16 is always fully open and communicates with the through hole Y120.

Further, at the first application point Y129 in the vicinity of the portion of the first fixed portion Y121 connected to the plurality of first ribs Y123, the electrical wiring Y6 passing through the through hole Y14 of the first outer layer Y11 shown in FIG. 20 The Y1 side end of the micro valve is connected. Further, the microvalve Y1 side end of the electric wiring Y7 passing through the through hole Y15 of the first outer layer Y11 shown in FIG. 20 is connected to the second application point Y130 of the second fixing portion Y122.

[Operation of valve module Y0]
Here, the operation of the valve module Y0 will be described. When the energization of the micro valve Y1 is started, a voltage is applied between the electrical wirings Y6 and Y7 to the first application point Y129 and the second application point Y130. Then, a current flows through the plurality of first ribs Y123 and the plurality of second ribs Y124. Due to this current, the plurality of first ribs Y123 and the plurality of second ribs Y124 generate heat. As a result, each of the plurality of first ribs Y123 and the plurality of second ribs Y124 expands in the longitudinal direction thereof.

As a result of such thermal expansion, the plurality of first ribs Y123 and the plurality of second ribs Y124 urge the spine Y125 toward the connection position YP2. The urged spine Y125 pushes the beam Y127 at the connection position YP2. In this way, the connection position YP2 corresponds to the urging position and the pressure adjusting urging position.

Then, the member composed of the beam Y127 and the arm Y126 integrally changes its posture with the hinge YP0 as a fulcrum and the connection position YP2 as a force point. As a result, the movable portion Y128 connected to the end of the beam Y127 opposite to the arm Y126 also moves in the longitudinal direction to the side where the spine Y125 pushes the beam Y127.

When the energization of the micro valve Y1 is stopped, the voltage application from the electrical wirings Y6 and Y7 to the first application point Y129 and the second application point Y130 is stopped. Then, the current stops flowing through the plurality of first ribs Y123 and the plurality of second ribs Y124, and the temperatures of the plurality of first ribs Y123 and the plurality of second ribs Y124 decrease. As a result, each of the plurality of first ribs Y123 and the plurality of second ribs Y124 contracts in the longitudinal direction thereof.

As a result of such thermal contraction, the plurality of first ribs Y123 and the plurality of second ribs Y124 urge the spine Y125 to the side opposite to the connection position YP2. The urged spine Y125 pulls the beam Y127 at the connection position YP2. As a result, the member including the beam Y127 and the arm Y126 integrally changes its posture with the hinge YP0 as the fulcrum and the connection position YP2 as the force point. As a result, the movable portion Y128 connected to the end of the beam Y127 opposite to the arm Y126 also moves in the longitudinal direction to the side where the spine Y125 pulls the beam Y127. As a result of the movement, the movable portion Y128 stops at a predetermined non-energized position.

When the microvalve Y1 is energized, the greater the power supplied from the electrical wirings Y6 and Y7 to the microvalve Y1 via the first application point Y129 and the second application point Y130, the more the movable portion with respect to the non-energized position. The amount of movement of Y128 also increases. This is because the higher the electric power supplied to the micro valve Y1, the higher the temperature of the first rib Y123 and the second rib Y124, and the greater the degree of expansion.

For example, when the voltage applied from the electrical wirings Y6 and Y7 to the first application point Y129 and the second application point Y130 is PWM controlled, the larger the duty ratio, the larger the amount of movement of the movable portion Y128 with respect to the non-energized state.

As shown in FIGS. 22 and 23, when the movable portion Y128 is in the non-energized position, the through holes Y120 are the first refrigerant holes Y16 and the third refrigerant holes Y18 in the direction orthogonal to the plate surface of the intermediate layer Y12. Although it overlaps, it does not overlap with the second refrigerant hole Y17 in the relevant direction. The second refrigerant hole Y17 overlaps the movable portion Y128 in the direction orthogonal to the plate surface of the intermediate layer Y12. That is, at this time, the first refrigerant hole Y16 and the third refrigerant hole Y18 are fully opened with respect to the through hole Y120, and the second refrigerant hole Y17 is fully closed. Therefore, in this case, the first refrigerant hole Y16 communicates with the third refrigerant hole Y18 via the movable portion Y128, and the second refrigerant hole Y17 is blocked from both the first refrigerant hole Y16 and the third refrigerant hole Y18. As a result, the flow of the refrigerant between the first communication hole YV1 and the third communication hole YV3 via the flow path Y81, the first refrigerant hole Y16, the through hole Y120, the third refrigerant hole Y18, and the flow path Y83. It will be possible.

Further, as shown in FIGS. 24 and 25, when the movable portion Y128 is located at the position farthest from the non-energized position due to the energization of the micro valve Y1, the position of the movable portion Y128 at that time is referred to as the maximum energized position. .. When the movable portion Y128 is in the maximum energized position, the electric power supplied to the micro valve Y1 becomes the maximum within the control range. For example, when the movable portion Y128 is in the maximum energized position, the duty ratio becomes the maximum value (for example, 100%) within the control range in the above-mentioned PWM control.

When the movable portion Y128 is in the maximum energized position, the through hole Y120 overlaps the first refrigerant hole Y16 and the second refrigerant hole Y17 in the direction orthogonal to the plate surface of the intermediate layer Y12, but the third refrigerant hole Y17 is in that direction. It does not overlap with Y18. The third refrigerant hole Y18 overlaps the movable portion Y128 in the direction orthogonal to the plate surface of the intermediate layer Y12. That is, at this time, the first refrigerant hole Y16 and the second refrigerant hole Y17 are fully opened with respect to the through hole Y120, and the third refrigerant hole Y18 is fully closed. Therefore, in this case, the first refrigerant hole Y16 communicates with the second refrigerant hole Y17 via the movable portion Y128, and the third refrigerant hole Y18 is blocked from both the first refrigerant hole Y16 and the second refrigerant hole Y17. As a result, the flow of the refrigerant between the first communication hole YV1 and the second communication hole YV2 via the flow path Y81, the first refrigerant hole Y16, the through hole Y120, the second refrigerant hole Y17, and the flow path Y83. It will be possible.

Further, by adjusting the electric power supplied to the micro valve Y1 by, for example, PWM control, the movable portion Y128 can be stopped at any intermediate position between the non-energized position and the maximum energized position. For example, in order to stop the movable portion Y128 at a position equidistant from the maximum energized position and the non-energized position (that is, the central position), the electric power supplied to the micro valve Y1 is the maximum value within the control range. It should be half. For example, the duty ratio of PWM control may be 50%.

When the movable portion Y128 is stopped at an intermediate position, the first refrigerant hole Y16, the second refrigerant hole Y17, and the third refrigerant hole Y18 all communicate with the through hole Y120. However, the second refrigerant hole Y17 and the third refrigerant hole Y18 are not fully opened with respect to the through hole Y120, and have an opening degree of less than 100% and larger than 0%. As the movable portion Y128 approaches the position at the maximum potential at the intermediate position, the opening degree of the third refrigerant hole Y18 with respect to the through hole Y120 decreases, and the opening degree of the second refrigerant hole Y17 increases.

The microvalve Y1 functions as a lever in which the beam Y127 and the arm Y126 have a hinge YP0 as a fulcrum, a connection position YP2 as a force point, and a connection position YP3 as an action point. As described above, the linear distance from the hinge YP0 to the connection position YP3 is longer than the linear distance from the hinge YP0 to the connection position YP2 in the plane parallel to the plate surface of the intermediate layer Y12. Therefore, the amount of movement of the connection position YP3, which is the point of action, is larger than the amount of movement of the connection position YP2, which is the point of effort. Therefore, the amount of displacement due to thermal expansion is amplified by the lever and transmitted to the movable portion Y128.

Further, the flow path of the refrigerant in the micro valve Y1 has a U-turn structure. Specifically, the refrigerant flows into the micro valve Y1 from one surface of the micro valve Y1, passes through the micro valve Y1, and flows out of the micro valve Y1 from the same surface of the micro valve Y1. Similarly, the flow path of the refrigerant in the valve module Y0 also has a U-turn structure. Specifically, the refrigerant flows into the valve module Y0 from one surface of the valve module Y0, passes through the valve module Y0, and flows out of the valve module Y0 from the same side surface of the valve module Y0. The direction orthogonal to the plate surface of the intermediate layer Y12 is the stacking direction of the first outer layer Y11, the intermediate layer Y12, and the second outer layer Y13.

Here, in the valve module Y0, the first refrigerant hole Y16 communicates with the opening degree adjusting chamber 286 via the first communication hole YV1 and the through hole 287a of the first recess 287. Further, the second refrigerant hole Y17 communicates with the inside of the upstream fitting hole 281 via the second communication hole YV2 and the through hole 288a of the second recess 288. Then, the third refrigerant hole Y18 communicates with the inside of the downstream fitting hole 282 via the through hole 289a of the third communication hole YV3 and the third recess 289.

Therefore, for example, when the movable portion Y128 of the micro valve Y1 is in the non-energized position, the first refrigerant hole Y16 and the third refrigerant hole Y18 communicate with each other, and the opening degree adjusting chamber 286 becomes the downstream fitting hole 282. Communicate. As a result, the pressure of the opening degree adjusting chamber 286 (that is, the control pressure Pm) is reduced to the low pressure Pl equivalent to the downstream fitting hole 282.

When the movable portion Y128 approaches the maximum energized position from the non-energized position by energizing the micro valve Y1 from this state, the refrigerant holes Y16, Y17, and Y18 communicate with each other, and the opening adjustment chamber 286 is fitted on the upstream side. It communicates with the hole 281 and the downstream fitting hole 282. As a result, the pressure of the opening degree adjusting chamber 286 (that is, the control pressure Pm) becomes an intermediate pressure larger than the low pressure pressure Pl and smaller than the high pressure pressure Ph.

Further, when the movable portion Y128 is in the position at the time of maximum energization by energizing the micro valve Y1, the first refrigerant hole Y16 and the second refrigerant hole Y17 communicate with each other, and the opening degree adjusting chamber 286 communicates with the upstream fitting hole 281. Communicate. As a result, the pressure of the opening degree adjusting chamber 286 (that is, the control pressure Pm) becomes a high pressure pressure Ph equivalent to that of the upstream fitting hole 281.

In consideration of these factors, in the refrigeration cycle device 10 of the present embodiment, the control pressure Pm is changed by changing the voltage applied to the microvalve Y1 by PWM control. For example, as shown in FIG. 26, the refrigeration cycle apparatus 10 increases the control pressure Pm by increasing the duty ratio of PWM control, and decreases the control pressure Pm by decreasing the duty ratio of PWM control.

In the first battery decompression unit 16 described above, the drive member of the main valve body 285 is composed of the valve module Y0. This valve module Y0 is smaller than a solenoid valve or an electric valve because the main valve body 285 is displaced to the valve opening side or the valve closing side by adjusting the pressure of the opening adjustment chamber 286 by the micro valve Y1. Can be configured in. One of the reasons is that the microvalve Y1 is formed of a semiconductor chip as described above. Further, as described above, the displacement amount due to thermal expansion can be amplified by using a lever, which makes it possible to configure the valve to be smaller than an electromagnetic valve or an electric valve that does not use such a lever.

Specifically, the micro valve Y1 has a configuration in which the opening degree of the second refrigerant hole Y17 and the third refrigerant hole Y18 is adjusted by the movable portion Y128 to change the pressure of the opening degree adjusting chamber 286. According to this, the main valve body 285 can be displaced to the valve closing side and the valve opening side by adjusting the pressure of the opening degree adjusting chamber 286 by the micro valve Y1.

According to this, the flow rate of the refrigerant can be adjusted to an appropriate amount according to the load conditions and the like by changing the throttle opening degree of the decompression unit 16 for the first battery. That is, in the refrigerating cycle device 10 of the present embodiment, the refrigerant and the refrigerating machine oil can be distributed in a desired ratio to the evaporators 15, 17 and 19 connected in parallel, as in the first embodiment. ..

Further, since the micro valve Y1 uses a lever, the amount of displacement due to thermal expansion can be suppressed from the amount of movement of the movable part Y128, so that the power consumption for driving the movable part Y128 can also be reduced. it can. Further, since the impact noise when the solenoid valve is driven can be eliminated, the noise can be reduced. Further, since the displacement of the plurality of first ribs Y123 and the plurality of second ribs Y124 is generated due to heat, the noise reduction effect is high.

Further, since the micro valve Y1 and the valve module Y0 have a refrigerant flow path having a U-turn structure, it is possible to reduce the digging of the block body 28. That is, the depth of the recess formed in the block body 28 for arranging the valve module Y0 can be suppressed. The reason is as follows.

For example, the valve module Y0 does not have a refrigerant flow path having a U-turn structure, the valve module Y0 has a refrigerant inlet on the surface on the block body 28 side, and the valve module Y0 has a refrigerant outlet on the opposite surface. Suppose. In that case, it is necessary to form refrigerant flow paths on both sides of the valve module Y0. Therefore, when trying to accommodate the refrigerant flow paths on both sides of the valve module Y0 in the block body 28, the dent that must be formed in the block body 28 in order to arrange the valve module Y0 becomes deep. Further, since the micro valve Y1 itself is small, the digging of the block body 28 can be further reduced.

Further, when the electrical wirings Y6 and Y7 are arranged on the surface of both sides of the micro valve Y1 opposite to the surface on which the first refrigerant holes Y16 and the second refrigerant holes Y17 are formed, the electrical wirings Y6 and Y7 are placed in the atmosphere. Can be placed closer to the atmosphere. Therefore, a seal structure such as a hermetic for reducing the influence of the refrigerant atmosphere on the electric wirings Y6 and Y7 becomes unnecessary. As a result, the decompression portions 14, 16 and 18 can be downsized.

Further, since the micro valve Y1 is lightweight, the pressure reducing portions 14, 16 and 18 are reduced in weight. Since the power consumption of the micro valve Y1 is small, the power saving units 14, 16 and 18 are reduced.

(Sixth Embodiment)
Next, the sixth embodiment will be described. In this embodiment, the micro valve X1 of the first embodiment is modified to have a failure detection function. Specifically, in addition to the same configuration as in the first and second embodiments, the micro valve X1 includes a failure detection unit X50 for detecting a failure of the micro valve X1 as shown in FIGS. 27 and 28.

The failure detection unit X50 includes a bridge circuit formed on the arm X126 of the intermediate layer X12. The bridge circuit includes four gauge resistors connected as shown in FIG. That is, the failure detection unit X50 is a bridge circuit whose resistance changes according to the distortion of the arm X126 corresponding to the diaphragm. That is, the failure detection unit X50 is a semiconductor piezoresistive distortion sensor. The failure detection unit X50 may be connected to the arm X126 via an electrical insulating film so as not to be electrically connected to the arm X126.

Wiring X51 and X52 are connected to two input terminals on the diagonal of this bridge circuit. Then, a voltage for generating a constant current is applied from the wirings X51 and X52 to the input terminal. The wirings X51 and X52 branch from the voltage applied to the microvalve X1 (that is, the microvalve drive voltage) via the electrical wirings X6 and X7 and extend to the above two input terminals.

Further, the wirings X53 and X54 are connected to two output terminals on different diagonals of the bridge circuit. Then, a voltage signal at a level corresponding to the amount of distortion of the arm X126 is output from the wirings X53 and X54. As will be described later, this voltage signal is used as information for determining whether or not the microvalve X1 is operating normally. The voltage signals output from the wirings X53 and X54 are input to the external control device X55 outside the microvalve X1.

The external control device X55 may be, for example, the control device 100 of the refrigeration cycle device 10. Alternatively, the external control device X55 may be a meter ECU that displays the vehicle speed, the remaining fuel amount, the remaining battery level, and the like in the vehicle.

When the external control device X55 acquires a voltage signal corresponding to the amount of distortion of the arm X126 via the wirings X53 and X54, the external control device X55 detects the presence or absence of failure of the microvalve X1 according to the voltage signal. Examples of the failure to be detected include a failure in which the arm X126 breaks, a failure in which a minute foreign substance is caught between the movable portion X128 and the first outer layer X11 or the second outer layer X13, and the movable portion X128 becomes immobile.

When the beam X127 and the movable portion X128 are displaced according to the expansion and contraction of the plurality of first ribs X123 and the plurality of second ribs X124, the amount of strain of the arm X126 changes. Therefore, the position of the movable portion X128 can be estimated from the voltage signal corresponding to the amount of distortion of the arm X126. On the other hand, if the micro valve X1 is normal, there is also a correlation between the amount of electricity supplied from the electrical wirings X6 and X7 to the micro valve X1 and the position of the movable portion X128. This energizing amount is a control amount for controlling the micro valve X1.

The external control device X55 utilizes this to detect the presence or absence of a failure of the micro valve X1. That is, the external control device X55 calculates the position of the movable portion X128 from the voltage signals from the wirings X53 and X54 based on the predetermined first map. Then, based on the second map determined in advance, the power supplied from the electric wirings X6 and X7 required to realize the position in the normal state to the micro valve X1 is calculated from the position of the movable portion X128. These first map and second map are recorded in the non-volatile memory of the external control device X55. Non-volatile memory is a non-transitional substantive storage medium. The correspondence between the level and the position of the voltage signal in the first map may be determined in advance by an experiment or the like. Further, the correspondence relationship between the position and the supplied power in the second map may be determined in advance by an experiment or the like.

Then, the external control device X55 compares the calculated electric power with the electric power actually supplied from the electric wirings X6 and X7 to the microvalve X1. Then, the external control device X55 determines that the micro valve X1 is out of order if the absolute value of the difference between the former power and the latter power exceeds the permissible value, and if it does not exceed the permissible value, the micro valve X1 is micro. It is determined that the valve X1 is normal. Then, when it is determined that the micro valve X1 is out of order, the external control device X55 performs predetermined failure notification control.

In this failure notification control, the external control device X55 operates a notification device X56 that notifies a person in the vehicle. For example, the external control device X55 may turn on the warning lamp. Further, the external control device X55 may cause the image display device to display an image indicating that the micro valve X1 has failed. As a result, the occupant of the vehicle can notice the failure of the micro valve X1.

Further, in this failure notification control, the external control device X55 may record information indicating that a failure has occurred in the micro valve X1 in the storage device in the vehicle. This storage device is a non-transitional substantive storage medium. As a result, the failure of the micro valve X1 can be recorded.

Further, the external control device X55 performs energization stop control when it is determined that the micro valve X1 is out of order. In the energization stop control, the external control device X55 stops the energization from the electric wires X6 and X7 to the micro valve X1. In this way, by stopping the energization of the micro valve X1 when the micro valve X1 fails, the safety of the micro valve X1 at the time of failure can be enhanced.

As described above, the failure detection unit X50 outputs a voltage signal for determining whether or not the micro valve X1 is operating normally, so that the external control device X55 determines whether or not the micro valve X1 has a failure. It can be easily identified.

Further, this voltage signal is a signal corresponding to the amount of distortion of the arm X126. Therefore, it is possible to easily determine the presence or absence of a failure of the micro valve X1 based on the relationship between the amount of electricity supplied from the electric wires X6 and X7 to the micro valve X1 and this voltage signal.

In this embodiment, it is determined whether or not the microvalve X1 is out of order based on the change in the resistance constituting the bridge circuit. However, as another method, it may be determined whether or not the microvalve X1 has failed based on the change in capacitance. In this case, a plurality of electrodes forming a capacitive component are formed on the arm X126 instead of the bridge circuit. There is a correlation between the amount of strain in the arm X126 and the capacitance between the plurality of electrodes. Therefore, the external control device X55 can determine whether or not the microvalve X1 has failed based on the change in capacitance between the plurality of electrodes.

(7th Embodiment)
Next, the seventh embodiment will be described. In this embodiment, the microvalve Y1 of the fifth embodiment is modified to have a failure detection function. Specifically, the microvalve Y1 includes a failure detection unit Y50 as shown in FIGS. 29 and 30 in addition to the same configuration as that of the fifth embodiment.

The failure detection unit Y50 includes a bridge circuit formed on the arm Y126 of the intermediate layer Y12. The bridge circuit includes four gauge resistors connected as shown in FIG. That is, the failure detection unit Y50 is a bridge circuit whose resistance changes according to the distortion of the arm Y126 corresponding to the diaphragm. That is, the failure detection unit Y50 is a semiconductor piezoresistive distortion sensor. The failure detection unit Y50 may be connected to the arm Y126 via an electrical insulating film so as not to be electrically connected to the arm Y126.

Wiring Y51 and Y52 are connected to two input terminals on the diagonal of the bridge circuit. Then, a voltage for generating a constant current is applied from the wirings Y51 and Y52 to the input terminal. The wirings Y51 and Y52 branch from the voltage applied to the microvalve Y1 (that is, the microvalve driving voltage) via the electrical wirings Y6 and Y7 and extend to the above two input terminals.

Further, the wirings Y53 and Y54 are connected to two output terminals on different diagonals of the bridge circuit. Then, a voltage signal corresponding to the amount of distortion of the arm Y126 is output from the wirings Y53 and Y54. As will be described later, this voltage signal is used as information for determining whether or not the microvalve Y1 is operating normally. The voltage signals output from the wirings Y53 and Y54 are input to the external control device Y55 outside the microvalve Y1.

The external control device Y55 may be, for example, the control device 100 of the refrigeration cycle device 10. Alternatively, the external control device Y55 may be a meter ECU that displays the vehicle speed, the remaining fuel amount, the remaining battery level, and the like in the vehicle.

When the external control device Y55 acquires a voltage signal corresponding to the amount of distortion of the arm Y126 via the wirings Y53 and Y54, the external control device Y55 detects the presence or absence of failure of the microvalve Y1 according to the voltage signal. Examples of the failure to be detected include a failure in which the arm Y126 breaks, a failure in which a minute foreign substance is caught between the movable portion Y128 and the first outer layer Y11 or the second outer layer Y13, and the movable portion Y128 becomes immobile.

When the beam Y127 and the movable portion Y128 are displaced according to the expansion and contraction of the plurality of first ribs Y123 and the plurality of second ribs Y124, the amount of strain of the arm Y126 changes. Therefore, the position of the movable portion Y128 can be estimated from the voltage signal corresponding to the amount of distortion of the arm Y126. On the other hand, if the micro valve Y1 is normal, there is also a correlation between the amount of electricity supplied from the electrical wirings Y6 and Y7 to the micro valve Y1 and the position of the movable portion Y128. This energizing amount is a control amount for controlling the micro valve Y1.

The external control device Y55 utilizes this to detect the presence or absence of failure of the microvalve Y1. That is, the external control device Y55 calculates the position of the movable portion Y128 from the voltage signals from the wirings Y53 and Y54 based on the predetermined first map. Then, based on the second map determined in advance, the power supplied from the electric wirings Y6 and Y7 required to realize the position in the normal state to the microvalve Y1 is calculated from the position of the movable portion Y128. These first map and second map are recorded in the non-volatile memory of the external control device Y55. Non-volatile memory is a non-transitional substantive storage medium. The correspondence between the level and the position of the voltage signal in the first map may be determined in advance by an experiment or the like. Further, the correspondence relationship between the position and the supplied power in the second map may be determined in advance by an experiment or the like.

Then, the external control device Y55 compares the calculated electric power with the electric power actually supplied from the electric wirings Y6 and Y7 to the microvalve Y1. Then, the external control device Y55 determines that the micro valve Y1 is out of order if the absolute value of the difference between the former power and the latter power exceeds the permissible value, and if it does not exceed the permissible value, the micro valve Y1 is micro. It is determined that the valve Y1 is normal. Then, when the external control device Y55 determines that the micro valve Y1 is out of order, the external control device Y55 performs predetermined failure notification control.

In this failure notification control, the external control device Y55 operates a notification device Y56 that notifies a person in the vehicle. For example, the external control device Y55 may turn on the warning lamp. Further, the external control device Y55 may cause the image display device to display an image indicating that the micro valve Y1 has failed. As a result, the occupant of the vehicle can notice the failure of the micro valve Y1.

Further, in this failure notification control, the external control device Y55 may record information indicating that a failure has occurred in the microvalve Y1 in the storage device in the vehicle. This storage device is a non-transitional substantive storage medium. As a result, the failure of the micro valve Y1 can be recorded.

Further, when the external control device Y55 determines that the micro valve Y1 is out of order, the external control device Y55 performs energization stop control. In the energization stop control, the external control device Y55 stops the energization from the electric wires Y6 and Y7 to the micro valve Y1. In this way, by stopping the energization of the micro valve Y1 when the micro valve Y1 fails, the safety of the micro valve Y1 at the time of failure can be enhanced.

As described above, the failure detection unit Y50 outputs a voltage signal for determining whether or not the microvalve Y1 is operating normally, so that the external control device Y55 determines whether or not the microvalve Y1 has a failure. It can be easily identified.

Further, this voltage signal is a signal corresponding to the amount of distortion of the arm Y126. Therefore, it is possible to easily determine whether or not the microvalve Y1 is out of order based on the relationship between the amount of electricity supplied from the electrical wirings Y6 and Y7 to the microvalve Y1 and this voltage signal.

In the present embodiment, it is determined whether or not the microvalve Y1 has failed based on the change in the resistance constituting the bridge circuit. However, as another method, it may be determined whether or not the microvalve Y1 has failed based on the change in capacitance. In this case, a plurality of electrodes forming a capacitive component are formed on the arm Y126 instead of the bridge circuit. There is a correlation between the amount of strain in the arm Y126 and the capacitance between the plurality of electrodes. Therefore, the external control device Y55 can determine whether or not the microvalve Y1 has failed based on the change in capacitance between the plurality of electrodes.

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

In the above-described first embodiment and the like, the throttle opening of each of the pressure reducing portions 14, 16 and 18 can be adjusted in two stages by opening and closing the micro valve X1, but the present invention is not limited to this. Each of the pressure reducing units 14, 16 and 18 may have, for example, a plurality of microvalves X1, and the throttle opening degree may be adjusted in a plurality of stages by switching the open / closed state of the plurality of microvalves X1.

The micro valve X1 of the first embodiment and the like described above may be configured not as a normally closed valve having a minimum throttle opening when not energized, but as a normally open valve having a maximum throttle opening when not energized. In this case, each of the pressure reducing portions 14, 16 and 18 has a large opening opening S2 when the micro valve X1 is not energized, and a small opening opening S1 when the micro valve X1 is energized.

As in the above-described embodiment, it is desirable, but not limited to, each of the decompression portions 14, 16 and 18 has a valve casing X2 interposed between the microvalve X1 and the block body. Each of the pressure reducing portions 14, 16 and 18 may be configured such that the micro valve X1 and the block body are in contact with each other without passing through the valve casing X2, for example. Further, the valve casing X2 is not limited to resin. Further, an additional member capable of absorbing the difference in the coefficient of linear expansion may be interposed between the valve casing X2 and the block body. These things are the same for the micro valve Y1.

In the above-described embodiment, a plurality of first ribs X123, a plurality of second ribs X124, a plurality of first ribs Y123, and a plurality of second ribs Y124 are energized to generate heat, and the heat generated by the heat generation itself. It expands as the temperature of the air rises. However, these members may be made of a shape memory material whose length changes as the temperature changes.

In the above-described embodiment, the decompression units 14, 16 and 18 are provided with the valve module Y0, but the present invention is not limited to this. The refrigeration cycle device 10 may be configured such that at least one of the decompression units 14, 16 and 18 is provided with the valve module Y0.

In the above-described embodiment, in the refrigerating cycle device 10 of the present disclosure, those in which the air supplied to the vehicle interior and the battery BT are targeted for cooling are exemplified, but the present invention is not limited thereto. The refrigeration cycle device 10 may be subject to cooling other than the air supplied to the vehicle interior and the battery BT.

Needless to say, in the above-described embodiment, the elements constituting the embodiment are not necessarily essential except when it is clearly stated that they are essential and when they are clearly considered to be essential in principle.

In the above-described embodiment, when numerical values such as the number, numerical value, amount, range, etc. of the components of the embodiment are mentioned, when it is clearly stated that it is particularly essential, and in principle, it is clearly limited to a specific number. Except in cases, it is not limited to the specific number.

In the above-described embodiment, when referring to the shape, positional relationship, etc. of a component or the like, the shape, positional relationship, etc., unless otherwise specified or in principle limited to a specific shape, positional relationship, etc. Not limited to, etc. For example, the shape and size of the micro valve X1 are not limited to those shown in the above embodiment. The micro valve X1 may have a first refrigerant hole X16 and a second refrigerant hole X17 having a hydraulic diameter that can control a very small flow rate and do not clog minute dust existing in the flow path. This also applies to the micro valve Y1.

In the above-described embodiment, when it is described that the external environment information of the vehicle (for example, the humidity outside the vehicle) is acquired from the sensor, the sensor is abolished and the external environment information is received from the server or the cloud outside the vehicle. It is also possible. Alternatively, it is possible to abolish the sensor, acquire related information related to the external environmental information from a server or cloud outside the vehicle, and estimate the external environmental information from the acquired related information.

The controls and methods thereof described in the present disclosure are realized by a dedicated computer provided by configuring a processor and memory programmed to perform one or more functions embodied by a computer program. May be done. Alternatively, the controls and methods thereof described in the present disclosure may be implemented by a dedicated computer provided by configuring the processor with one or more dedicated hardware logic circuits. Alternatively, the control unit and method thereof described in the present disclosure may be a combination of a processor and memory programmed to perform one or more functions and a processor composed of one or more hardware logic circuits. It may be realized by one or more dedicated computers configured. Further, the computer program may be stored in a computer-readable non-transitional tangible recording medium as an instruction executed by the computer.

(Summary)
According to the first aspect shown in some or all of the above embodiments, in a refrigeration cycle apparatus, at least one of the plurality of decompression portions is a variable decompression unit including a valve component for adjusting a throttle opening. Is. In the valve parts, the base part where the fluid chamber through which the refrigerant flows is formed, the drive part that is displaced by the temperature change, the amplification part that amplifies the displacement due to the temperature change of the drive part, and the displacement amplified by the amplification part are transmitted. It has a moving part that adjusts the refrigerant pressure in the fluid chamber by moving. The amplification unit is configured to function as a lever with the hinge as the fulcrum, the amplification unit as the force point at the urging position urged by the drive unit, and the connection position between the amplification unit and the movable unit as the action point. ing.

According to the second aspect, the variable decompression unit includes a fixed diaphragm having a fixed opening degree. At the base, a first fluid hole serving as an inlet for the refrigerant in the fluid chamber and a second fluid hole serving as an outlet for the refrigerant in the fluid chamber are formed. The valve component is configured to adjust the throttle opening of the variable depressurizing portion by switching the communication and blocking of the first fluid hole and the second fluid hole by the movable portion.

In this way, if the variable decompression section includes not only the valve component but also the fixed throttle, the throttle opening of the variable decompression section is stepped by switching the communication and blocking of the first fluid hole and the second fluid hole in the valve component. Can be adjusted. Further, when the variable pressure reducing unit includes a fixed throttle, the valve component is not driven when it is not necessary to adjust the throttle opening of the variable pressure reducing unit, thereby reducing the driving frequency of the valve component and reducing the variable pressure reducing unit. Energy consumption can be suppressed.

According to the third aspect, a first fluid hole serving as an inlet for the refrigerant in the fluid chamber and a second fluid hole serving as an outlet for the refrigerant in the fluid chamber are formed in the base portion. The valve component not only switches the communication and blocking of the first fluid hole and the second fluid hole by the movable part, but also adjusts the opening degree of at least one of the first fluid hole and the second fluid hole by the movable part. By doing so, the throttle opening of the variable decompression unit is adjusted. In this way, if the valve component is configured as a variable throttle in which the throttle opening of the decompression section can be changed, the throttle opening of the decompression section can be adjusted to a desired opening by changing the opening of the fluid hole in the valve component. Can be adjusted.

According to the fourth aspect, in the refrigeration cycle device, at least one of the plurality of decompression units is a variable decompression unit whose throttle opening degree can be adjusted. The variable decompression unit includes a block body in which an inlet flow path, a valve chamber, a throttle flow path, and an outlet flow path are formed, a main valve body, and a drive member for driving the main valve body. An opening degree adjusting chamber is formed in the block body. The drive member includes a valve component for adjusting the pressure in the opening degree adjusting chamber. In the valve parts, the base part where the fluid chamber through which the refrigerant flows is formed, the drive part that is displaced by the temperature change, the amplification part that amplifies the displacement due to the temperature change of the drive part, and the displacement amplified by the amplification part are transmitted. It has a movable part that adjusts the refrigerant pressure in the opening degree adjusting chamber by moving. The amplification unit is configured to function as a lever with the hinge as the fulcrum, the amplification unit as the force point at the urging position urged by the drive unit, and the connection position between the amplification unit and the movable unit as the action point. ing.

According to the fifth aspect, the base includes a first fluid hole for communicating the fluid chamber and the opening degree adjusting chamber, a second fluid hole for communicating the fluid chamber and the inlet flow path, and a fluid chamber and the outlet flow path. A third fluid hole is formed to communicate with the fluid. The valve component not only opens and closes the second fluid hole and the third fluid hole by the movable part, but also adjusts the opening degree of at least one of the second fluid hole and the third fluid hole by the movable part. It is configured to change the pressure in the opening adjustment chamber.

According to this, the pressure in the opening adjustment chamber can be finely adjusted, and the flow rate of the refrigerant can be adjusted to an appropriate amount according to the load conditions, etc., so that the capacity of the heat exchanger on the user side of the radiator and evaporator can be made more efficient. It will be possible to demonstrate it in good condition.

According to the sixth aspect, the variable pressure reducing portion includes a component mounting portion for mounting the valve component on the object to be mounted to which the valve component is mounted. The component mounting portion is interposed between the component mounting portion and the valve component so that the valve component and the object to be mounted do not come into direct contact with each other. In this way, if the component mounting portion is interposed between the object to be mounted and the valve component, the component mounting portion functions as a cushioning material, so that the valve component can be protected.

According to the seventh aspect, the component mounting portion is configured such that the coefficient of linear expansion of the component mounting portion is a value between the coefficient of linear expansion of the valve component and the coefficient of linear expansion of the object to be mounted. .. According to this, even if thermal strain occurs due to a temperature change of the object to be mounted, the stress of the thermal strain due to the temperature change of the object to be mounted is absorbed by the component mounting portion, so that the valve component can be protected. ..

According to the eighth viewpoint, the object to be attached is a block body that connects the refrigerant inlet portion of the variable evaporator connected to the downstream side of the refrigerant flow of the variable decompression unit and the refrigerant pipe among the plurality of evaporators. is there. The valve component is integrally configured with the variable evaporator by being attached to the block body via the component mounting portion.

According to this, the high-temperature and high-pressure refrigerant before passing through the decompression section flows through the refrigerant pipe. In such a configuration, when the refrigerant flows through the refrigerant pipe, heat can be dissipated around the refrigerant pipe, so that the endothermic capacity of the evaporator can be improved. Such a configuration is suitable when the evaporator is used as a heat exchanger on the user side.

According to the ninth aspect, the plurality of evaporators include a cooling evaporator for cooling the air supplied to the room and a battery evaporator for cooling the chargeable / discharging battery. A pressure adjusting valve for maintaining the pressure on the refrigerant outlet side of the battery evaporator at a predetermined pressure is provided on the refrigerant outlet side of the battery evaporator. According to this, for example, when cooling the battery and cooling the passenger compartment at the same time, it is possible to reduce the pressure of the refrigerant passing through the cooling evaporator while maintaining the pressure of the refrigerant passing through the battery evaporator. ..

According to the tenth aspect, the plurality of evaporators include a cooling evaporator for cooling the air supplied to the room and a battery evaporator for cooling the chargeable / discharging battery. A pressure adjusting valve for maintaining the pressure on the refrigerant outlet side of the cooling evaporator at a predetermined pressure is provided on the refrigerant outlet side of the cooling evaporator.

According to this, for example, when cooling the battery and cooling the passenger compartment at the same time, it is possible to reduce the pressure of the refrigerant passing through the battery evaporator while maintaining the pressure of the refrigerant passing through the cooling evaporator. ..

According to the eleventh viewpoint, the valve component includes a failure detection unit that outputs a signal for determining whether the valve component is operating normally or failing. When the valve component outputs such a signal, it is possible to easily determine whether or not the valve component has a failure.

According to the twelfth viewpoint, the signal output by the valve component is a signal corresponding to the amount of distortion of the amplification unit. In this way, it is possible to determine the presence or absence of a failure of the valve device based on the relationship between this signal and the control amount for controlling the valve component.

According to the thirteenth aspect, the drive unit generates heat when energized, and the failure detection unit outputs a signal to a device that stops energization of the valve component when the valve component fails. In this way, by stopping the energization when the valve component fails, the safety at the time of failure can be enhanced.

According to the fourteenth viewpoint, the failure detection unit outputs a signal to a device that operates a notification device that notifies a person when a valve component is out of order. Thereby, a person can know the failure of the valve component.

According to the fifteenth aspect, the valve component is composed of a semiconductor chip. According to this, the valve component can be made compact.

11 Compressor 12 Heat radiator 14, 16, 18 Cooling decompression unit, 1st battery decompression unit, 2nd battery decompression unit 15, 17, 19 Cooling evaporator, 1st battery evaporator, 2nd battery Evaporator X1 micro valve (valve parts)
X11, X121, X13 Base X123, X124, X125 Drive X126, X127 Amplifier X128 Movable part

Claims (15)

It is a refrigeration cycle device
A compressor (11) that compresses and discharges the refrigerant,
A radiator (12) that dissipates heat from the refrigerant discharged from the compressor, and
On the downstream side of the refrigerant flow of the radiator, a plurality of decompression units (14, 16, 18) connected in parallel with each other
A plurality of evaporators (15, 17, 19) connected to the downstream side of the refrigerant flow of each of the plurality of decompression units and evaporating the refrigerant decompressed by the decompression unit are provided.
At least one of the plurality of decompression portions is a variable decompression portion (14, 16, 18) including a valve component (X1) for adjusting the throttle opening degree.
The valve parts
Bases (X11, X12, X13) on which a fluid chamber (X19) through which at least a part of the refrigerant that has passed through the radiator flows flows, and
Drive units (X123, X124, X125) that displace when their temperature changes,
Amplifying units (X126, X127) that amplify the displacement due to changes in the temperature of the driving unit,
It has a movable part (X128) that adjusts the pressure of the refrigerant in the fluid chamber by transmitting and moving the displacement amplified by the amplification part.
When the drive unit is displaced due to a change in temperature, the drive unit biases the amplification unit at the urging position (XP2), so that the amplification unit is displaced with the hinge (XP0) as a fulcrum and the above. At the connection position (XP3) between the amplification unit and the movable portion, the amplification portion urges the movable portion.
A refrigeration cycle device in which the distance from the hinge to the connection position is longer than the distance from the hinge to the urging position. The variable decompression unit includes a fixed diaphragm (170) having a fixed opening degree.
A first fluid hole (X16) serving as an inlet for the refrigerant in the fluid chamber and a second fluid hole (X17) serving as an outlet for the refrigerant in the fluid chamber are formed in the base portion.
The valve component has a configuration according to claim 1, wherein the valve component is configured to adjust the throttle opening degree of the variable decompression unit by switching the communication and blocking of the first fluid hole and the second fluid hole by the movable portion. Refrigeration cycle equipment. A first fluid hole (X16) serving as an inlet for the refrigerant in the fluid chamber and a second fluid hole (X17) serving as an outlet for the refrigerant in the fluid chamber are formed in the base portion.
The valve component not only switches the communication and blocking of the first fluid hole and the second fluid hole by the movable portion, but also by the movable portion, at least one of the first fluid hole and the second fluid hole. The refrigeration cycle device according to claim 1, wherein the throttle opening of the variable decompression unit is adjusted by adjusting the opening of the fluid hole. It is a refrigeration cycle device
A compressor (11) that compresses and discharges the refrigerant,
A radiator (12) that dissipates heat from the refrigerant discharged from the compressor, and
On the downstream side of the refrigerant flow of the radiator, a plurality of decompression units (14, 16, 18) connected in parallel with each other
A plurality of evaporators (15, 17, 19) connected to the downstream side of the refrigerant flow of each of the plurality of decompression units and evaporating the refrigerant decompressed by the decompression unit are provided.
At least one of the plurality of decompression units is a variable decompression unit (14, 16, 18) whose throttle opening degree can be adjusted.
The variable decompression unit
An inlet flow path (281) into which the refrigerant that has passed through the radiator flows in, a valve chamber (283) that communicates with the inlet flow path, a throttle flow path (284) that reduces and expands the refrigerant that has flowed into the valve chamber, and the throttle. A block body (28) having an outlet flow path (282) for discharging the refrigerant that has passed through the flow path toward the evaporator.
A main valve body (285) housed in the valve chamber and adjusting the throttle opening in the throttle flow path,
A driving member (X0) for driving the main valve body is included.
The block body is formed with an opening degree adjusting chamber (286) into which a refrigerant for pressing the main valve body to the valve opening side or the valve closing side is introduced.
The drive member includes a valve component (Y1) for adjusting the pressure in the opening degree adjusting chamber.
The valve parts
The bases (Y11, Y12, Y13) on which the fluid chamber (Y19) through which the refrigerant introduced into the opening degree adjusting chamber flows flows, and
Drive units (Y123, Y124, Y125) that displace when their temperature changes,
Amplifying units (Y126, Y127) that amplify the displacement due to changes in the temperature of the driving unit, and
It has a movable part (Y128) that adjusts the pressure of the refrigerant flowing through the fluid chamber by transmitting and moving the displacement amplified by the amplification part.
When the drive unit is displaced due to a change in temperature, the drive unit biases the amplification unit at the urging position (YP2), so that the amplification unit is displaced with the hinge (YP0) as a fulcrum and the above. The amplification unit urges the movable portion at the connection position (YP3) between the amplification unit and the movable portion.
A refrigeration cycle device in which the distance from the hinge to the connection position is longer than the distance from the hinge to the urging position. The base includes a first fluid hole (Y16) that communicates the fluid chamber and the opening degree adjusting chamber, a second fluid hole (Y17) that communicates the fluid chamber and the inlet flow path, and the fluid chamber. A third fluid hole (Y17) that communicates with the outlet flow path is formed.
The valve component not only opens and closes the second fluid hole and the third fluid hole by the movable portion, but also uses the movable portion to open and close the second fluid hole and at least one of the third fluid holes. The refrigerating cycle apparatus according to claim 4, wherein the pressure in the opening degree adjusting chamber is changed by adjusting the opening degree. The variable decompression unit includes a component mounting portion (X3, Y3) for mounting the valve component on an object to be mounted (27, 28) to which the valve component is mounted.
The component mounting portion is one of claims 1 to 5, wherein the component mounting portion is interposed between the component mounting portion and the valve component so that the valve component and the object to be mounted do not come into direct contact with each other. The refrigeration cycle device described. 6. The component mounting portion is configured such that the linear expansion coefficient of the component mounting portion is a value between the linear expansion coefficient of the valve component and the linear expansion coefficient of the object to be mounted. The refrigeration cycle device according to. When the variable evaporator is connected to the downstream side of the refrigerant flow of the variable decompression section among the plurality of evaporators.
The object to be attached is a joint (27C) that connects the refrigerant inlet portion of the variable evaporator and the refrigerant pipe (26).
The refrigeration cycle apparatus according to claim 6 or 7, wherein the valve component is integrally formed with the variable evaporator by being attached to the joint via the component mounting portion. The plurality of evaporators include a cooling evaporator (15) for cooling the air supplied to the room, and a battery evaporator (17, 19) for cooling a chargeable / discharging battery (BT). And
Any one of claims 1 to 8, wherein a pressure adjusting valve (20) for maintaining the pressure on the refrigerant outlet side of the battery evaporator at a predetermined pressure is provided on the refrigerant outlet side of the battery evaporator. The refrigeration cycle apparatus according to one. The plurality of evaporators include a cooling evaporator (15) for cooling the air supplied to the room, and a battery evaporator (17, 19) for cooling a chargeable / discharging battery (BT). And
Any one of claims 1 to 8, wherein a pressure adjusting valve (20A) for maintaining the pressure on the refrigerant outlet side of the cooling evaporator at a predetermined pressure is provided on the refrigerant outlet side of the cooling evaporator. The refrigeration cycle apparatus according to one. Any one of claims 1 to 10, wherein the valve component includes a failure detection unit (X50, Y50) that outputs a signal for determining whether the valve component is operating normally or has a failure. The refrigeration cycle device according to one. The refrigeration cycle apparatus according to claim 11, wherein the signal is a signal corresponding to the amount of distortion of the amplification unit. The drive unit generates heat when energized,
The refrigeration cycle device according to claim 11 or 12, wherein the failure detection unit outputs the signal to a device (X55, Y55) that stops energization of the valve component when the valve component is out of order. The failure detection unit outputs the signal to a device (X55, Y55) that operates a notification device (X56, Y56) that notifies a person when the valve component is out of order. 12. The refrigeration cycle device according to 12. The refrigeration cycle apparatus according to any one of claims 1 to 14, wherein the valve component is composed of a semiconductor chip.

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