JP6992777B2 - Refrigeration cycle device, evaporation pressure control valve - Google Patents

Description

The present disclosure relates to an evaporative pressure regulating valve for adjusting the pressure on the refrigerant outlet side of the evaporator and a refrigeration cycle device including the pressure regulating valve.

Conventionally, in a steam compression type refrigeration cycle device, an evaporation pressure adjusting valve for maintaining the pressure on the refrigerant outlet side of the evaporator may be arranged between the evaporator and the compressor. The evaporation pressure adjusting valve is configured to increase the valve opening degree (that is, the refrigerant passage area) as the flow rate of the refrigerant flowing through the evaporator increases.

The evaporative pressure regulating valve is disclosed in, for example, Patent Document 1. Patent Document 1 discloses a so-called bellows type pressure regulating valve. The pressure regulating valve described in Patent Document 1 includes a valve body that adjusts the flow path opening of the refrigerant flow path inside the body, a bellows in which a predetermined gas is sealed, and a spring arranged inside the bellows. It is configured.

Japanese Patent Application Laid-Open No. 2015-152137

By the way, in the bellows type pressure regulating valve described in Patent Document 1, the valve body is displaced by the balance between the refrigerant pressure of the evaporator, the pressure of the gas inside the bellows, and the elastic force of the bellows and the spring. In the evaporative pressure regulating valve having such a structure, when the displacement amount of the valve body increases as the flow rate of the refrigerant flowing through the evaporator increases, not only the elastic force of the spring but also the elastic force of the bellows and the gas inside the bellows The pressure also increases. For this reason, when it is necessary to increase the endothermic capacity of the evaporator, for example, at the start of cooling operation, the pressure regulating valve operates on the valve closing side, and the endothermic effect of the evaporator may not be properly exhibited. be.

As a countermeasure, for example, the evaporative pressure adjusting valve may be configured to drive the valve body by an electric motor such as a stepping motor, and the valve body of the evaporative pressure adjusting valve may be forcibly displaced to the fully open position during cooling operation or the like. Conceivable.

However, the evaporative pressure adjusting valve that drives the valve body with an electric motor has a very large physique. This is not preferable because it causes deterioration of mountability.

It is an object of the present disclosure to provide an evaporation pressure regulating valve and a refrigerating cycle apparatus capable of appropriately exerting the endothermic effect of an evaporator while suppressing deterioration of mountability.

The invention according to claim 1 is
It ’s a refrigeration cycle device.
Compressors (11, Z11) that compress and discharge the refrigerant, and
A radiator (12, Z12) that dissipates the heat of the refrigerant discharged from the compressor,
On the downstream side of the refrigerant flow of the radiator, a plurality of decompression units (15a, 15b, Z14, Z16) connected so as to be in parallel with each other,
A plurality of evaporators (16, 18, Z15, Z17) connected to the downstream side of the refrigerant flow of each of the plurality of decompression sections and evaporating the decompressed refrigerant in the decompression section.
It is provided with an evaporation pressure adjusting valve (19), which is connected to the refrigerant outlet side of some of the plurality of evaporators and maintains the refrigerant pressure of some of the evaporators at a predetermined value or higher.
The evaporative pressure adjusting valve switches between an adjusted state in which the throttle opening is adjusted according to the refrigerant pressure of some evaporators and a fully open state in which the throttle opening is fully opened regardless of the refrigerant pressure of some evaporators. Includes function switching unit (X0),
The function switching unit (X0) includes a valve component (X1) for adjusting the throttle opening.
Valve parts
A base (X11, X12, X13) forming a fluid chamber (X19) through which at least a portion of the refrigerant that has passed through some evaporator flows.
The drive unit (X123, X124, X125) that displaces when its own 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 flow rate 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 urges 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. The amplification part urges the movable part at the connection position (XP3) of
The distance from the hinge to the connection position is longer than the distance from the hinge to the urging position.

According to this, the function switching unit makes it possible to switch the evaporation pressure adjusting valve from the adjusted state to the fully open state. Therefore, for example, when it is necessary to increase the endothermic capacity of the evaporator on the upstream side of the evaporation pressure adjusting valve, the endothermic effect of the evaporator can be appropriately exerted by switching the evaporation pressure adjusting valve to the fully open state. can.

In addition, since the amplification part of the valve component of the function switching part functions as a lever, the displacement amount according to the temperature change of the drive part is amplified by the lever and transmitted to the movable part. As described above, a valve component whose displacement amount due to thermal expansion is amplified by using a lever can be configured to be smaller than an electromagnetic valve or an electric valve that does not use such a lever.

Therefore, according to the refrigerating cycle apparatus of the present disclosure, it is possible to appropriately exert the endothermic effect of the evaporator while suppressing the deterioration of the mountability.

The invention according to claim 9 is
An evaporation pressure adjusting valve for maintaining the refrigerant pressure of the evaporator (18) constituting the refrigerating cycle apparatus (10) above a predetermined value.
Refrigerant inflow path (41) into which the refrigerant that has passed through the evaporator flows in, a valve chamber (43) in which the refrigerant flows in from the refrigerant inflow path, and a refrigerant outflow path that causes the refrigerant to flow out from the valve chamber to the refrigerant suction side of the compressor (11). The body portion (40) on which (42) is formed and
A passage forming member (44) arranged in the valve chamber to form a communication passage (430) for communicating the refrigerant inflow passage and the refrigerant outflow passage, and to form a cylinder chamber (440) inside the communication passage.
A main valve body (45) that is slidably arranged with respect to the cylinder chamber and adjusts the throttle opening of the communication passage by receiving the refrigerant pressure in the refrigerant inflow passage.
An elastic member (46) that applies an urging force to the main valve body so as to oppose the refrigerant pressure in the refrigerant inflow path acting on the main valve body.
It is equipped with a function switching unit (X0) that switches between an adjusted state in which the throttle opening is adjusted according to the refrigerant pressure of the evaporator and a fully open state in which the throttle opening is fully opened regardless of the refrigerant pressure in the evaporator.
The cylinder chamber is divided into a first pressure chamber (440a) communicating with the refrigerant inflow passage and a second pressure chamber (440b) communicating with the refrigerant outflow passage by the main valve body.
The first pressure chamber and the second pressure chamber communicate with each other through the pressure equalizing passage (451a).
The main valve body is arranged in the cylinder chamber so as to be displaced according to the pressure difference between the first pressure chamber and the second pressure chamber.
The function switching unit includes a valve component (X1) for adjusting the pressure difference between the first pressure chamber and the second pressure chamber.
Valve parts
A fluid chamber (X19) through which the refrigerant flows, a first fluid hole (X16) communicating the second pressure chamber and the fluid chamber, and a second fluid hole (X17) communicating the fluid chamber and the refrigerant outflow path are formed. With the base (X11, X12, X13),
The drive unit (X123, X124, X125) that displaces when its own 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 opening degree of the second fluid hole 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 urges 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. The amplification part urges the movable part at the connection position (XP3) of
The distance from the hinge to the connection position is longer than the distance from the hinge to the urging position.

According to this, the evaporation pressure adjusting valve can be switched from the adjusted state to the fully open state by adjusting the pressure difference between the first pressure chamber and the second pressure chamber by the valve parts. Therefore, for example, when it is necessary to increase the endothermic capacity of the evaporator, the endothermic effect of the evaporator can be appropriately exerted by switching the evaporation pressure adjusting valve to the fully open state.

Since the amplification part of the valve component functions as a lever, the amount of displacement corresponding to the temperature change of the drive part is amplified by the lever and transmitted to the moving part. As described above, a valve component whose displacement amount due to thermal expansion is amplified by using a lever can be configured to be smaller than an electromagnetic valve or an electric valve that does not use such a lever.

Therefore, according to the evaporative pressure regulating valve of the present disclosure, it is possible to appropriately exert the endothermic effect of the evaporator while suppressing the deterioration of the mountability.

The 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.

FIG. 3 is a schematic configuration diagram of a vehicle air conditioner including a refrigeration cycle device including an evaporation pressure adjusting valve according to the first embodiment. It is a schematic cross-sectional view of the evaporative pressure control valve which concerns on 1st Embodiment. It is a schematic sectional drawing which shows the adjustment state of the evaporation pressure adjustment valve which concerns on 1st Embodiment. It is a schematic cross-sectional view which shows the fully open state of the evaporation pressure control valve which concerns on 1st Embodiment. It is explanatory drawing for demonstrating the relationship between the operation mode of the refrigerating cycle apparatus which concerns on 1st Embodiment, and the state of the evaporation pressure control valve. It is a schematic disassembled perspective view of the micro valve used for the evaporation pressure control valve which concerns on 1st Embodiment. It is a schematic side view of the micro valve used for the evaporation pressure control valve which concerns on 1st Embodiment. FIG. 7 is a cross-sectional view showing a VIII-VIII cross section of FIG. 7, showing a closed state of the microvalve. It is sectional drawing which shows the IX-IX cross section of FIG. FIG. 7 shows a cross section taken along the line XX of FIG. 7, and is a cross-sectional view showing a valve opened state of the microvalve. It is sectional drawing which shows the XI-XI cross section of FIG. It is explanatory drawing for demonstrating operation of the micro valve used for the evaporation pressure control valve which concerns on 1st Embodiment. It is explanatory drawing for demonstrating the relationship between the series dehumidification heating mode and the state of an evaporating pressure control valve. It is a schematic block diagram of the in-vehicle cooling apparatus provided with the refrigerating cycle apparatus including the evaporation pressure control valve which concerns on 2nd Embodiment. It is explanatory drawing for demonstrating the relationship between the operation mode of the refrigerating cycle apparatus which concerns on 2nd Embodiment, and the state of the evaporation pressure control valve. It is a schematic diagram which shows the inside of the micro valve used for the evaporation pressure control valve which concerns on 3rd 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 given to parts that are the same as or equal 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 is not particularly hindered, even if not explicitly stated.

This embodiment will be described with reference to FIGS. 1 to 12. In this embodiment, an example in which the evaporation pressure adjusting valve 19 is applied to the refrigerating cycle device 10 of the vehicle air conditioner 1 will be described. The vehicle air conditioner 1 is mounted on a hybrid vehicle that obtains a driving force for vehicle traveling from an internal combustion engine and a traveling electric motor. The refrigeration cycle device 10 functions in the vehicle air conditioner 1 to cool or heat the blown air blown into the vehicle interior, which is the space to be air-conditioned.

The vehicle air conditioner 1 will be described with reference to FIG. As shown in FIG. 1, the vehicle air conditioner 1 includes a refrigeration cycle device 10, an indoor air conditioner unit 30, and a control device 100.

The refrigerating cycle device 10 is configured to be able to switch between a cooling mode refrigerant circuit, a heating mode refrigerant circuit, and a dehumidifying heating mode refrigerant circuit. In FIG. 1, the flow of the refrigerant in the refrigerant circuit in the heating mode is indicated by the arrow FLa, and the flow of the refrigerant in the refrigerant circuit in the cooling mode is indicated by the arrow FLb. Further, in FIG. 1, the flow of the refrigerant in the refrigerant circuit in the dehumidifying / heating mode is indicated by an arrow FLc.

The refrigeration cycle device 10 employs an HFC-based refrigerant (specifically, R134a) as the refrigerant. Of course, as the refrigerant, an HFO-based refrigerant (for example, R1234yf), a natural refrigerant (for example, R744), or the like may be adopted.

The refrigeration cycle device 10 includes a compressor 11, an indoor condenser 12, a first expansion valve 15a, a second expansion valve 15b, an outdoor heat exchanger 16, a check valve 17, an indoor evaporator 18, an evaporation pressure adjusting valve 19, and an accumulator. 20, It has a first on-off valve 21, a second on-off valve 22, and the like.

The compressor 11 sucks in the refrigerant in the refrigerating cycle device 10, compresses and discharges the refrigerant, and is arranged in the vehicle bonnet. The compressor 11 is configured as an electric compressor in which a fixed capacity type compression unit having a fixed discharge capacity is driven by an electric motor. 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 described later.

The refrigerant inlet side of the indoor condenser 12 is connected to the discharge port of the compressor 11. The indoor condenser 12 functions as a radiator that dissipates heat from the refrigerant in the heating mode and the dehumidifying heating mode. Specifically, the indoor condenser 12 exchanges heat between the high-temperature and high-pressure discharged refrigerant discharged from the compressor 11 and the blown air that has passed through the indoor evaporator 18, which will be described later, in the heating mode and the dehumidifying heating mode. It is a heat exchanger for heating that heats the blown air. The indoor condenser 12 is arranged in the casing 31 of the indoor air conditioning unit 30, which will be described later.

One inflow outlet side of the first three-way joint 13a is connected to the refrigerant outlet of the indoor condenser 12. The first three-way joint 13a functions as a branching portion or a merging portion in the refrigeration cycle device 10. The first three-way joint 13a may be formed by joining a plurality of pipes, or may be formed by providing a plurality of refrigerant passages in a metal block or a resin block. The second three-way joint 13b, the third three-way joint 13c, and the fourth three-way joint 13d, which will be described later, have the same configuration as that of the first three-way joint 13a.

The first three-way joint 13a is connected to the first refrigerant passage 14a to one of the pair of inflow outlets constituting the refrigerant outlet, and to the second refrigerant passage 14b to the other. The first refrigerant passage 14a is a refrigerant passage that guides the refrigerant flowing out of the indoor condenser 12 to the refrigerant inlet side of the outdoor heat exchanger 16. The second refrigerant passage 14b is a refrigerant passage that guides the refrigerant flowing out of the indoor condenser 12 to the inlet side of the second expansion valve 15b arranged in the third refrigerant passage 14c, which will be described later.

A first expansion valve 15a is arranged in the first refrigerant passage 14a. The first expansion valve 15a is a refrigerant decompression device that depressurizes the refrigerant flowing out of the indoor condenser 12 in the heating mode and the dehumidifying heating mode. The first expansion valve 15a is a variable throttle having a valve body configured so that the throttle opening degree can be changed and an electric motor such as a stepping motor that changes the throttle opening degree of the valve body.

Further, the first expansion valve 15a is configured as a variable throttle with a fully open function that functions as a mere refrigerant passage without exerting a refrigerant depressurizing action by fully opening the throttle opening. The operation of the first expansion valve 15a is controlled by a control signal output from the control device 100.

The refrigerant inlet side of the outdoor heat exchanger 16 is connected to the outlet side of the first expansion valve 15a, and is arranged on the vehicle front side in the vehicle bonnet. The outdoor heat exchanger 16 exchanges heat between the refrigerant flowing out from the first expansion valve 15a and the vehicle outdoor air (that is, outside air).

The outdoor heat exchanger 16 evaporates the refrigerant decompressed by the first expansion valve 15a by exchanging heat with the outside air, for example, in the heating mode and the dehumidifying heating mode. Further, for example, in the cooling mode, the outdoor heat exchanger 16 exchanges heat with the outside air for the refrigerant that has passed through the first expansion valve 15a to dissipate heat. As described above, the outdoor heat exchanger 16 functions as an evaporator that absorbs heat from the outside air and evaporates the refrigerant in the heating mode and the dehumidifying heating mode, and functions as a radiator that dissipates heat to the outside air in the cooling mode.

One inflow outlet of the second three-way joint 13b is connected to the refrigerant outlet side of the outdoor heat exchanger 16. A third refrigerant passage 14c is connected to another inflow port of the second three-way joint 13b. The third refrigerant passage 14c guides the refrigerant flowing out of the outdoor heat exchanger 16 to the refrigerant inlet side of the indoor evaporator 18.

A fourth refrigerant passage 14d is connected to yet another inflow port of the second three-way joint 13b. The fourth refrigerant passage 14d guides the refrigerant flowing out of the outdoor heat exchanger 16 to the inlet side of the accumulator 20, which will be described later.

In the third refrigerant passage 14c, a check valve 17, a third three-way joint 13c, and a second expansion valve 15b are arranged in this order with respect to the refrigerant flow. The check valve 17 only allows the refrigerant to flow from the second three-way joint 13b side to the indoor evaporator 18 side. The above-mentioned second refrigerant passage 14b is connected to the third three-way joint 13c.

The second expansion valve 15b depressurizes the refrigerant flowing out of the outdoor heat exchanger 16 and flowing into the indoor evaporator 18. That is, the second expansion valve 15b functions as a refrigerant decompression device. The basic configuration of the second expansion valve 15b is the same as that of the first expansion valve 15a. Further, the second expansion valve 15b is configured with a variable throttle having a fully closed function that closes the refrigerant passage when the throttle opening is fully closed.

The refrigerating cycle device 10 can switch the refrigerant circuit by fully closing the second expansion valve 15b and closing the third refrigerant passage 14c. In other words, the second expansion valve 15b has a function as a refrigerant depressurizing device and also a function as a circuit switching device for switching the refrigerant circuit of the refrigerant circulating in the cycle.

The indoor evaporator 18 functions as an evaporator that evaporates the refrigerant in the cooling mode and the dehumidifying / heating mode. That is, the indoor evaporator 18 cools the blown air by exchanging heat with the blown air before passing through the indoor condenser 12 and evaporating the refrigerant flowing out from the second expansion valve 15b in the cooling mode and the dehumidifying / heating mode. .. The indoor evaporator 18 is arranged on the upstream side of the blast air flow of the indoor condenser 12 in the casing 31 of the indoor air conditioning unit 30.

The inlet side of the evaporation pressure adjusting valve 19 is connected to the refrigerant outlet side of the indoor evaporator 18. The evaporation pressure adjusting valve 19 functions to adjust the refrigerant evaporation pressure in the indoor evaporator 18 to a reference pressure higher than a reference pressure capable of suppressing frost formation in order to suppress frost formation in the indoor evaporator 18.

Specifically, when the pressure of the refrigerant in the indoor evaporator 18 drops below the reference pressure, the evaporation pressure adjusting valve 19 reduces the throttle opening (that is, the passage area of the refrigerant passage), and the pressure of the refrigerant becomes the reference pressure. When it exceeds, the throttle opening is increased. The flow rate of the refrigerant flowing through the indoor evaporator 18 increases or decreases according to the throttle opening degree of the evaporation pressure adjusting valve 19. Therefore, the evaporation pressure adjusting valve 19 also functions as a flow rate adjusting valve.

The evaporation pressure adjusting valve 19 is configured as a flow rate adjusting valve with a fully open function capable of fully opening the throttle opening regardless of the pressure of the refrigerant of the indoor evaporator 18. That is, the evaporation pressure adjusting valve 19 is fully opened so that the throttle opening is adjusted according to the pressure of the refrigerant of the indoor evaporator 18 and the throttle opening is fully opened regardless of the pressure of the refrigerant of the indoor evaporator 18. It is configured to be switchable between states. Switching between the adjusted state and the fully open state in the evaporative pressure adjusting valve 19 is controlled by the control device 100. The specific configuration of the evaporation pressure adjusting valve 19 will be described later.

A fourth three-way joint 13d is connected to the refrigerant outlet side of the evaporation pressure adjusting valve 19. Further, as described above, the fourth refrigerant passage 14d is connected to the other inflow port of the fourth three-way joint 13d. The inlet side of the accumulator 20 is connected to yet another inflow port of the fourth three-way joint 13d.

The accumulator 20 is a gas-liquid separator that separates the air-liquid of the refrigerant that has flowed into the inside and stores the surplus refrigerant in the cycle. The suction port side of the compressor 11 is connected to the gas phase refrigerant outlet of the accumulator 20. Therefore, the accumulator 20 functions to suppress the suction of the liquid phase refrigerant into the compressor 11 and prevent the liquid compression in the compressor 11.

Further, a first on-off valve 21 is arranged in the fourth refrigerant passage 14d connecting the second three-way joint 13b and the fourth three-way joint 13d. The first on-off valve 21 is composed of a solenoid valve. The first on-off valve 21 functions as a circuit switching device for switching the refrigerant circuit by opening and closing the fourth refrigerant passage 14d. The operation of the first on-off valve 21 is controlled by a control signal output from the control device 100.

Similarly, a second on-off valve 22 is arranged in the second refrigerant passage 14b connecting the first three-way joint 13a and the third three-way joint 13c. The second on-off valve 22 is configured by a solenoid valve like the first on-off valve 21. The second on-off valve 22 functions as a circuit switching device for switching the refrigerant circuit by opening and closing the second refrigerant passage 14b.

Next, the indoor air conditioning unit 30 will be described. The indoor air-conditioning unit 30 is for blowing out the blown air whose temperature has been adjusted by the refrigeration cycle device 10 into the vehicle interior. The indoor air conditioning unit 30 is arranged inside the instrument panel at the front of the vehicle interior.

The indoor air conditioning unit 30 is configured by accommodating a blower 32, an indoor evaporator 18, an indoor condenser 12, and the like in a casing 31 forming the outer shell thereof. The casing 31 forms an air passage for the blown air to be blown into the vehicle interior.

An inside / outside air switching device 33 is arranged on the most upstream side of the blast air flow in the casing 31. The inside / outside air switching device 33 is a device that switches between the inside air and the outside air, which are the interior air of the vehicle, into the casing 31.

A blower 32 is arranged on the downstream side of the blower air flow of the inside / outside air switching device 33. The blower 32 blows the air sucked through the inside / outside air switching device 33 toward the vehicle interior. The blower 32 is an electric blower that drives a centrifugal fan with an electric motor. The blower 32 is controlled by a control voltage output from the control device 100.

On the downstream side of the blower air flow of the blower 32, the indoor evaporator 18 and the indoor condenser 12 are arranged in this order with respect to the blower air flow. In other words, the indoor evaporator 18 is arranged on the upstream side of the blast air flow with respect to the indoor condenser 12.

Further, a cold air bypass passage 35 is formed in the casing 31. The cold air bypass passage 35 is a passage for allowing the blown air that has passed through the indoor evaporator 18 to bypass the indoor condenser 12 and flow to the downstream side.

An air mix door 34 is arranged on the downstream side of the blown air flow of the indoor evaporator 18 and on the upstream side of the blown air flow of the indoor condenser 12. The air mix door 34 is used to adjust the ratio of the air volume passing through the indoor condenser 12 to the air blown air after passing through the indoor evaporator 18. Therefore, in the vehicle air conditioner 1, the cold air bypass passage 35 is fully opened, and the air flow path of the blown air toward the indoor condenser 12 is completely closed by the air mix door 34, whereby the amount of heat exchange in the indoor condenser 12 is increased. Can be minimized.

Further, a mixing space is provided on the downstream side of the blown air flow of the indoor condenser 12. In the mixing space, the blown air heated by the indoor condenser 12 and the blown air that has passed through the cold air bypass passage 35 and has not been heated by the indoor condenser 12 are mixed. Further, a plurality of opening holes are arranged in the most downstream portion of the blast air flow of the casing 31. The blown air mixed in the mixed space is blown out into the vehicle interior, which is the air-conditioned space, through these opening holes.

Specifically, as these opening holes, a face opening hole, a foot opening hole, and a defroster opening hole are provided. The face opening hole is an opening hole for blowing air-conditioning air toward the upper body of the occupant in the vehicle interior. The foot opening hole is an opening hole for blowing air-conditioning air toward the feet of the occupant. The defroster opening hole is an opening hole for blowing air conditioning air toward the inner surface of the front window glass of the vehicle.

Although not shown, on the downstream side of the blast air flow of the face opening hole, the foot opening hole, and the defroster opening hole, the face outlet, the foot outlet, and the defroster outlet provided in the vehicle interior are provided through ducts forming air passages, respectively. It is connected to the exit. Further, a face door, a foot door, and a defroster door are arranged on the upstream side of the blast air flow of the face opening hole, the foot opening hole, and the defroster opening hole. The face door, foot door, and defroster door are connected to an electric motor, and their operation is controlled by a control signal output from the control device 100.

Next, the control device 100 of the vehicle air conditioner 1 will be described. The control device 100 includes a microprocessor including a processor, a memory, and the like, and a peripheral circuit thereof. The control device 100 performs various calculations and processes based on the control program stored in the memory, and controls the operation of various controlled target devices connected to the output side. The memory of the control device 100 is composed of a non-transitional substantive storage medium.

As described above, the vehicle air conditioner 1 can switch the operation mode to the heating mode, the cooling mode, and the dehumidifying heating mode. The control device 100 switches the operation mode to any of a heating mode, a cooling mode, and a dehumidifying heating mode according to, for example, an operation signal from an operation panel operated by the user. Hereinafter, the heating mode, the cooling mode, and the dehumidifying heating mode will be described.

(A) The heating mode control device 100 controls the first on-off valve 21 so that the fourth refrigerant passage 14d is opened when the operation mode is set to the heating mode, and the second refrigerant passage 14b is closed. The second on-off valve 22 is controlled so as to be so. Further, the control device 100 controls the second expansion valve 15b so that the third refrigerant passage 14c is closed. As a result, the refrigerating cycle device 10 is switched to the refrigerant circuit through which the refrigerant flows as shown by the arrow FLa in FIG.

With the configuration of this refrigerant circuit, the control device 100 determines the operating state of various control devices connected to the control device 100 based on the target blowout temperature TAO, the detection signal of the sensor group, and the like.

For example, regarding the control signal output to the servomotor of the air mix door 34, the air mix door 34 blocks the cold air bypass passage 35, and the total flow rate of the blown air after passing through the indoor evaporator 18 causes the indoor condenser 12. Determined to pass.

Further, the control signal output to the first expansion valve 15a is determined not to be in the fully open state but to have a throttle opening that exerts a depressurizing action. Further, regarding the evaporation pressure adjusting valve 19, it is determined that the evaporation pressure adjusting valve 19 is fully opened. In the heating mode, the third refrigerant passage 14c is closed by the second expansion valve 15b, so that the refrigerant does not flow into the indoor evaporator 18 and the evaporation pressure adjusting valve 19. Therefore, regarding the evaporation pressure adjusting valve 19, it may be determined that the evaporation pressure adjusting valve 19 is in the adjusted state.

The control device 100 outputs the control signals and the like determined as described above to various control devices. As a result, the high-pressure refrigerant discharged from the compressor 11 flows into the indoor condenser 12. The refrigerant that has flowed into the indoor condenser 12 is blown from the blower 32 and exchanges heat with the blown air that has passed through the indoor evaporator 18 to dissipate heat. As a result, the blown air is heated.

The refrigerant flowing out of the indoor condenser 12 flows into the first expansion valve 15a through the first refrigerant passage 14a, and is depressurized and expanded by the first expansion valve 15a until it becomes a low-pressure refrigerant. Then, the low-pressure refrigerant decompressed by the first expansion valve 15a flows into the outdoor heat exchanger 16 and absorbs heat from the outside air. The refrigerant flowing out of the outdoor heat exchanger 16 flows into the accumulator 20 via the fourth refrigerant passage 14d and is separated into gas and liquid. Then, the gas phase refrigerant separated by the accumulator 20 is sucked from the suction side of the compressor 11 and compressed again by the compressor 11.

As described above, in the heating mode, the heat of the high-pressure refrigerant discharged from the compressor 11 in the indoor condenser 12 can be dissipated to the air blown into the vehicle interior, and the heated blown air can be blown out into the vehicle interior. can. As a result, it is possible to realize heating in the vehicle interior. The heating mode is an operation mode in which the outdoor heat exchanger 16 exerts an endothermic action and the indoor evaporator 18 does not exert an endothermic action.

(B) The cooling mode control device 100 controls the first on-off valve 21 so that the fourth refrigerant passage 14d is closed when the operation mode is set to the cooling mode, and the second refrigerant passage 14b is closed. The second on-off valve 22 is controlled so as to be so. Further, the control device 100 controls the second expansion valve 15b so that the first refrigerant passage 14a is fully opened. As a result, the refrigerating cycle device 10 is switched to the refrigerant circuit through which the refrigerant flows as shown by the arrow FLb in FIG.

With the configuration of this refrigerant circuit, the control device 100 determines the operating state of various control devices connected to the control device 100 based on the target blowout temperature TAO, the detection signal of the sensor group, and the like.

For example, regarding the control signal output to the servomotor of the air mix door 34, it is determined that the total flow rate of the blown air after the air mix door 34 has passed through the indoor evaporator 18 passes through the cold air bypass passage 35.

Further, the control signal output to the second expansion valve 15b is determined not to be in the fully closed state but to have a throttle opening that exerts a depressurizing action. Further, regarding the evaporation pressure adjusting valve 19, it is determined that the evaporation pressure adjusting valve 19 is fully opened.

The control device 100 outputs the control signals and the like determined as described above to various control devices. As a result, the high-pressure refrigerant discharged from the compressor 11 flows into the indoor condenser 12. At this time, since the air mix door 34 blocks the air passage of the indoor condenser 12, the refrigerant flowing into the indoor condenser 12 flows out of the indoor condenser 12 with almost no heat exchange with the blown air.

The refrigerant flowing out of the indoor condenser 12 flows into the first expansion valve 15a through the first refrigerant passage 14a. At this time, since the first expansion valve 15a is in the fully open state of the first refrigerant passage 14a, the refrigerant flowing out of the indoor condenser 12 is not decompressed by the first expansion valve 15a and is transferred to the outdoor heat exchanger 16. Inflow. Then, the refrigerant flowing into the outdoor heat exchanger 16 is dissipated to the outside air by the outdoor heat exchanger 16.

The refrigerant flowing out of the outdoor heat exchanger 16 flows into the second expansion valve 15b via the third refrigerant passage 14c, and is decompressed and expanded by the second expansion valve 15b until it becomes a low-pressure refrigerant. The low-pressure refrigerant decompressed by the second expansion valve 15b flows into the indoor evaporator 18 and absorbs heat from the blown air blown from the blower 32 and evaporates. As a result, the blown air is cooled.

The refrigerant flowing out of the indoor evaporator 18 flows into the accumulator 20 and is gas-liquid separated. Then, the gas phase refrigerant separated by the accumulator 20 is sucked from the suction side of the compressor 11 and compressed again by the compressor 11.

As described above, in the cooling mode, since the air passage of the indoor condenser 12 is blocked by the air mix door 34, the blown air cooled by the indoor evaporator 18 can be blown out into the vehicle interior. As a result, it is possible to realize cooling in the vehicle interior. The cooling mode is an operation mode in which the indoor evaporator 18 exerts an endothermic action and the outdoor heat exchanger 16 does not exert an endothermic action.

Here, if the evaporation pressure adjusting valve 19 is in the adjusted state in the cooling mode, the evaporation pressure adjusting valve 19 is closed when it is necessary to increase the endothermic capacity of the indoor evaporator 18, for example, immediately after the start of cooling. It may operate on the valve side. In this case, the pressure on the refrigerant outlet side of the indoor evaporator 18 rises more than necessary, and the endothermic effect of the indoor evaporator 18 is not properly exhibited.

On the other hand, in the cooling mode of the present embodiment, the evaporation pressure adjusting valve 19 is in the fully open state, so that the heat absorption of the indoor evaporator 18 is higher than that in the case where the evaporation pressure adjusting valve 19 is in the adjusted state. The effect can be exerted appropriately.

(C) The dehumidifying / heating mode control device 100 controls the first on-off valve 21 so that the fourth refrigerant passage 14d is opened when the operation mode is set to the dehumidifying / heating mode, and the second refrigerant passage 14b The second on-off valve 22 is controlled so as to be opened. As a result, the refrigerating cycle device 10 is switched to the refrigerant circuit through which the refrigerant flows as shown by the arrow FLc in FIG. In the dehumidifying / heating mode, the outdoor heat exchanger 16 and the indoor evaporator 18 are connected in parallel with respect to the refrigerant flow.

With the configuration of this refrigerant circuit, the control device 100 determines the operating state of various control devices connected to the control device 100 based on the target blowout temperature TAO, the detection signal of the sensor group, and the like.

For example, regarding the control signal output to the servomotor of the air mix door 34, it is determined that the air mix door 34 blocks the cold air bypass passage 35 as in the heating mode.

Further, the control signals output to the first expansion valve 15a and the second expansion valve 15b are determined so as to have a predetermined throttle opening for the dehumidifying / heating mode defined in advance. Further, regarding the evaporation pressure adjusting valve 19, it is determined that the evaporation pressure adjusting valve 19 is in the adjusted state.

The control device 100 outputs the control signals and the like determined as described above to various control devices. As a result, the high-pressure refrigerant discharged from the compressor 11 flows into the indoor condenser 12. The refrigerant that has flowed into the indoor condenser 12 is blown from the blower 32 and exchanges heat with the blown air that has passed through the indoor evaporator 18 to dissipate heat. As a result, the blown air is heated.

The refrigerant flowing out of the indoor condenser 12 flows into the first expansion valve 15a through the first refrigerant passage 14a, and also flows into the second expansion valve 15b through the second refrigerant passage 14b and the third refrigerant passage 14c. ..

The high-pressure refrigerant flowing into the first expansion valve 15a is depressurized until it becomes a low-pressure refrigerant. Then, the low-pressure refrigerant decompressed by the first expansion valve 15a flows into the outdoor heat exchanger 16 and absorbs heat from the outside air. On the other hand, the high-pressure refrigerant flowing into the second expansion valve 15b is depressurized until it becomes a low-pressure refrigerant. Then, the low-pressure refrigerant decompressed by the second expansion valve 15b flows into the indoor evaporator 18 and absorbs heat from the air blown from the blower 32 to evaporate. As a result, the blown air is cooled.

The refrigerant flowing out of the outdoor heat exchanger 16 and the refrigerant flowing out of the indoor evaporator 18 merge upstream of the accumulator 20, then flow from the accumulator 20 to the suction side of the compressor 11 and are compressed again by the compressor 11. To.

As described above, in the dehumidifying / heating mode, the blown air dehumidified by the indoor evaporator 18 can be heated by the indoor condenser 12 and blown out into the vehicle interior. This makes it possible to realize dehumidifying and heating in the vehicle interior. The dehumidifying / heating mode is an operation mode in which the indoor evaporator 18 and the outdoor heat exchanger, which are connected in parallel, each exert an endothermic action.

Here, in the dehumidifying / heating mode, the evaporation pressure adjusting valve 19 is in the adjusted state, and the refrigerant pressure of the indoor evaporator 18 is adjusted to be equal to or higher than the reference pressure. Therefore, even if the outdoor heat exchanger 16 and the indoor evaporator 18 are connected in parallel, the refrigerant pressure in the outdoor heat exchanger 16 can be lower than the refrigerant pressure in the indoor evaporator 18.

Next, a specific configuration of the evaporative pressure regulating valve 19 will be described with reference to FIG. The evaporation pressure adjusting valve 19 is arranged between the indoor evaporator 18 and the compressor 11 in the refrigeration cycle device 10. The evaporation pressure adjusting valve 19 is adjusted so that the refrigerant pressure Pe in the indoor evaporator 18 becomes equal to or higher than a predetermined reference pressure (that is, the frost formation suppressing pressure APe).

The evaporative pressure regulating valve 19 includes a body portion 40 that forms an outer shell. The body portion 40 is made of a metal member made of an aluminum alloy or the like. Inside the body portion 40, a refrigerant inflow passage 41, a refrigerant outflow passage 42, and a connection space portion 43 connecting the refrigerant inflow passage 41 and the refrigerant outflow passage 42 are formed.

The refrigerant inflow path 41 is formed so as to extend linearly from one side surface of the body portion 40. The refrigerant inflow path 41 is a flow path through which the refrigerant from the indoor evaporator 18 flows. The refrigerant inflow path 41 is formed with a valve seat 411 to which the main valve body 45, which will be described later, comes into contact with and detaches from the connection portion with the connection space portion 43 which is the end portion on the downstream side of the refrigerant flow.

The refrigerant outflow passage 42 is formed so as to extend in the same direction as the refrigerant inflow passage 41 from the opposite side of the side surface of the body portion 40 where the refrigerant inflow passage 41 is formed. The refrigerant outflow path 42 is a flow path through which the refrigerant flows out toward the refrigerant suction side of the compressor 11 via the accumulator 20.

The connection space portion 43 is formed so as to connect the refrigerant inflow path 41 and the refrigerant outflow path 42. The refrigerant that has flowed in from the refrigerant inflow path 41 flows out from the refrigerant outflow path 42 toward the compressor 11 via the connection space 43.

In the connection space portion 43, a tubular passage forming portion 44 forming a communication passage 430 for communicating the refrigerant inflow passage 41 and the refrigerant outflow passage 42 is arranged between the connection space portion 43 and the inner wall forming the connection space portion 43. There is. The passage forming portion 44 is made of a metal member made of an aluminum alloy or the like, and is fixed to the inner wall forming the connection space portion 43.

Inside the passage forming portion 44, a cylinder chamber 440 in which the main valve body 45, which will be described later, is slidably arranged is formed. The passage forming portion 44 is composed of a bottomed tubular member 441 and a lid portion 442 that closes the opening of the tubular member 441. The tubular member 441 is arranged inside the connection space 43 so that the bottom surface is located on the refrigerant inflow path 41 side and the opening is located on the refrigerant outflow path 42 side. An insertion hole 441a through which the intermediate diameter portion 452 of the main valve body 45, which will be described later, is inserted is formed on the bottom surface of the tubular member 441.

Inside the tubular member 441, a main valve body 45 extending along the uniaxial center CL is housed so as to be displaceable in the axial DRa of the axial center CL. The axial DRa is in a direction that coincides with the arrangement direction of the refrigerant inflow path 41 and the refrigerant outflow path 42.

The main valve body 45 is configured in a cylindrical shape. The main valve body 45 has a large diameter portion 451 having an outer diameter similar to the inner diameter of the tubular member 441, and an intermediate diameter portion 452 having an outer diameter smaller than that of the large diameter portion 451 and having an outer diameter similar to that of the insertion hole 441a. It is configured to include a small diameter portion 453 having a smaller diameter than the intermediate diameter portion 452.

The main valve body 45 is a connecting body in which the large diameter portion 451, the intermediate diameter portion 452, and the small diameter portion 453 are connected in this order. The main valve body 45 is configured as an integrally molded product in which the large diameter portion 451 and the intermediate diameter portion 452 and the small diameter portion 453 are integrally molded. The main valve body 45 is arranged inside the tubular member 441 so that the small diameter portion 453 is located on the refrigerant inflow path 41 side and the large diameter portion 451 is located on the refrigerant outflow path 42 side.

The intermediate filament portion 452 constitutes a valve body whose end portion located on the refrigerant inflow path 41 side is in contact with and separated from the valve seat 411. Further, the large diameter portion 451 and the intermediate diameter portion 452 constitute a partition wall for dividing the cylinder chamber 440 inside the passage forming portion 44 into the inner pressure chamber 440a and the outer pressure chamber 440b. That is, the cylinder chamber 440 is divided into an inner pressure chamber 440a and an outer pressure chamber 440b by the main valve body 45. The inner pressure chamber 440a constitutes the first pressure chamber, and the outer pressure chamber 440b constitutes the second pressure chamber.

The inner pressure chamber 440a is a space formed inside the large diameter portion 451 and the intermediate diameter portion 452. The inner pressure chamber 440a communicates with the refrigerant inflow passage 41 via the refrigerant introduction passage 450 formed inside the small diameter portion 453.

The outer pressure chamber 440b is a space formed between the intermediate filament portion 452 and the tubular member 441. The outer pressure chamber 440b communicates with the inner pressure chamber 440a via a pressure equalizing passage 451a formed at a connection portion between the large diameter portion 451 and the intermediate diameter portion 452.

In the outer pressure chamber 440b, an elastic member 46 that urges the main valve body 45 to the refrigerant outflow path 42 side (that is, the other side of the axial DRa) is arranged. In other words, the elastic member 46 applies an urging force to the main valve body 45 so as to oppose the refrigerant pressure of the refrigerant inflow path 41 acting on the main valve body 45. The elastic member 46 is made of a cylindrical coil spring made of stainless steel or the like.

Further, the passage forming portion 44 is provided with a valve module X0 including a micro valve X1. The valve module X0 is an opening / closing member that switches between a communication state in which the outer pressure chamber 440b and the communication passage 430 are communicated by the micro valve X1 and a non-communication state in which the communication between the outer pressure chamber 440b and the communication passage 430 is cut off. Specifically, the micro valve X1 is a valve component for adjusting the pressure difference between the inner pressure chamber 440a and the outer pressure chamber 440b.

The valve module X0 is integrally attached to the body portion 40 and the passage forming portion 44. The body portion 40 and the passage forming portion 44 constitute an object to be attached to which the microvalve X1 is to be attached.

An insertion hole 47 through which a valve fixing portion X8, which will be described later, is inserted is formed on one side surface of the body portion 40. The insertion hole 47 is a through hole that penetrates the front and back of a part of the body portion 40 that forms the communication passage 430. Further, a fitting hole 443 into which a protrusion X21, which will be described later, is fitted is formed on one side surface of the passage forming portion 44. The fitting hole 443 is a through hole that penetrates the front and back of a part of the passage forming portion 44 that forms the outer pressure chamber 440b. The details of the valve module X0 will be described later.

When the outer pressure chamber 440b and the communication passage 430 are in a communicating state by the valve module X0, the evaporation pressure adjusting valve 19 configured as described above has a main valve body 45 according to a force acting on the main valve body 45. Is displaced. The displacement of the main valve body 45 changes the throttle opening of the evaporation pressure adjusting valve 19, so that the refrigerant pressure of the indoor evaporator 18 is adjusted to a desired state. The throttle opening degree of the evaporation pressure adjusting valve 19 is the throttle opening degree (that is, the passage area) of the communication passage 430 connecting the refrigerant inflow passage 41 and the refrigerant outflow passage 42.

Specifically, when the outer pressure chamber 440b and the communication passage 430 are in a communicating state by the valve module X0, the main valve body 45 has the refrigerant pressure Pe and the outer pressure of the refrigerant inflow passage 41 and the inner pressure chamber 440a. The refrigerant pressure Pm of the chamber 440b and the load of the elastic member 46 act on it. Since the refrigerant inflow passage 41 and the inner pressure chamber 440a communicate with each other via the introduction passage 450, the pressures are the same.

The main valve body 45 is displaced to a position where the load acting on the axial DRa is balanced with respect to itself, and the throttle opening degree of the evaporation pressure adjusting valve 19 is adjusted. The balance of the load acting on the main valve body 45 in the axial direction DRa can be expressed by, for example, the following mathematical formula F1.

Pe × Ab = Pe × Am + Pm × (Ab-Am) + K × L + F0 ... (F1)
In the above-mentioned formula F1, the refrigerant pressure of the refrigerant inflow path 41 and the inner pressure chamber 440a is indicated by Pe, and the refrigerant pressure of the outer pressure chamber 440b is indicated by Pm. Then, in the above-mentioned mathematical formula F1, the pressure receiving area of the large diameter portion 451 is indicated by Ab, and the pressure receiving area of the intermediate diameter portion 452 is indicated by Am. Further, in the above-mentioned mathematical formula F1, the spring constant of the elastic member 46 is indicated by K, the displacement amount of the main valve body 45 is indicated by L, and the initial load of the elastic member 46 is indicated by F0.

By modifying this formula F1, the refrigerant pressure Pe of the refrigerant inflow path 41 can be expressed by the following formula F2.

Pe = Pm + K × L / (Ab-Am) + F0 / (Ab-Am) ... (F2)
According to the equation F2, it can be seen that the refrigerant pressure Pe of the refrigerant inflow path 41 increases as the displacement amount L of the main valve body 45 increases. When the displacement amount L of the main valve body 45 increases, the throttle opening of the evaporation pressure adjusting valve 19 also increases, so that the flow rate of the refrigerant passing through the indoor evaporator 18 also increases.

Therefore, the evaporation pressure adjusting valve 19 evaporates as the displacement amount L of the main valve body 45 increases in proportion to the increase in the refrigerant pressure Pe of the refrigerant inflow path 41 and the refrigerant pressure Pe of the refrigerant inflow path 41 increases. The pressure regulating valve 19 is configured to increase the throttle opening.

On the other hand, in the evaporation pressure adjusting valve 19, when the outer pressure chamber 440b and the communication passage 430 are in a non-communication state by the valve module X0, the refrigerant pressure Pm of the outer pressure chamber 440b becomes the refrigerant pressure Pe of the inner pressure chamber 440a. Equivalent (ie, Pe = Pm). In this case, the main valve body 45 is displaced to the valve opening side by the load of the elastic member 26. That is, the main valve body 45 is displaced to the position where the throttle opening degree of the evaporation pressure adjusting valve 19 is maximized.

As described above, the evaporative pressure adjusting valve 19 is in the adjusted state shown in FIG. 3 when the outer pressure chamber 440b and the communication passage 430 are in a communicating state by the valve module X0, and is in a non-communication state. It is in the fully open state shown in FIG.

Further, as described above, the control device 100 controls the evaporation pressure adjusting valve 19 so as to be in the fully open state in the cooling mode and the heating mode, and controls the evaporation pressure adjusting valve 19 so as to be in the adjusted state in the dehumidifying and heating mode. do.

Therefore, as shown in FIG. 5, the control device 100 sets the valve module X0 so that the outer pressure chamber 440b and the communication passage 430 are in a non-communication state (that is, a closed state) in the cooling mode and the heating mode. Control. Further, the control device 100 controls the valve module X0 so that the outer pressure chamber 440b and the communication passage 430 are in a communication state (that is, an open state) in the dehumidifying / heating mode.

Here, when the outer pressure chamber 440b and the communication passage 430 are communicated with each other by the valve module X0, the evaporation pressure adjusting valve 19 is in an adjusting state in which the throttle opening degree is adjusted according to the refrigerant pressure of the indoor evaporator 18. .. Further, when the outer pressure chamber 440b and the communication passage 430 are in a non-communication state by the valve module X0, the evaporation pressure adjusting valve 19 is in a fully open state in which the throttle opening is fully opened regardless of the refrigerant pressure of the indoor evaporator 18. .. Therefore, the valve module X0 switches between an adjusted state in which the throttle opening is adjusted according to the refrigerant pressure of the indoor evaporator 18 and a fully open state in which the throttle opening is fully opened regardless of the refrigerant pressure in the indoor evaporator 18. Configure the function switching unit. Hereinafter, the configuration of the valve module X0 will be described.

[Valve module X0 configuration]
As shown in FIG. 2, the valve module X0 has a microvalve X1, a valve casing X2, a sealing member X3, one O-ring X4, two electrical wirings X6, X7, and a valve fixing portion X8.

The microvalve 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 configured in a small size. 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. Opening and closing is switched by switching between energization and non-energization of the micro valve X1. 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 fixing portion X8, and pass through the valve. It is connected to the power supply outside the module X0. As a result, 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 linear expansion coefficient is a value between the linear expansion coefficient of the microvalve X1 and the linear expansion coefficient of the passage forming portion 44. The valve casing X2 constitutes a component mounting portion for mounting the micro valve X1 to the passage forming portion 44.

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 passage forming portion 44 and the micro valve X1 so that the micro valve X1 and the passage forming portion 44 do not come into direct contact with each other. Then, one surface of the bottom wall is in contact with and fixed to the passage forming portion 44, and the other surface is in contact with and fixed to one of the two plate surfaces of the microvalve X1. In this way, the valve casing X2 can absorb the difference in the linear expansion coefficient between the micro valve X1 and the passage forming portion 44. This is because the linear expansion coefficient of the valve casing X2 is a value between the linear expansion coefficient of the microvalve X1 and the linear expansion coefficient of the passage forming portion 44.

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

The protrusion X21 is fitted into a fitting hole 443 formed in the passage forming portion 44. The protrusion X21 is formed with a first communication hole XV1 that penetrates from the end on the side of the microvalve X1 to the inner end of the fitting hole 443. Further, a second communication hole XV2 penetrating from the end on the side of the microvalve X1 to the inner end of the passage forming portion 44 is formed in the portion adjacent to the protruding portion X21.

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 sides 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 protrusion X21 and seals between the passage forming portion 44 and the protrusion X21 to suppress the leakage of the refrigerant to the outside of the evaporation pressure adjusting valve 19.

The valve fixing portion X8 is a portion for fixing the entire valve module X0 to the body portion 40. The valve fixing portion X8 is a concave box body having a bottom wall on one side and an open side on the other side. The valve fixing portion X8 is fixed to the valve casing X2 in a state where the bottom wall of the valve fixing portion X8 and the bottom wall of the valve casing X2 face each other. A space for accommodating the microvalve X1 is formed between the bottom wall of the valve fixing portion X8 and the bottom wall of the valve casing X2.

The valve fixing portion X8 is formed of the same type of resin as the valve casing X2. The valve fixing portion X8 is configured such that the linear expansion coefficient is a value between the linear expansion coefficient of the microvalve X1 and the linear expansion coefficient of the body portion 40. The valve fixing portion X8 constitutes a component mounting portion for mounting the micro valve X1 to the body portion 40.

The valve fixing portion X8 is fixed to the body portion 40 with its side wall inserted into the insertion hole 47 formed in the body portion 40. The valve fixing portion X8 is interposed between the body portion 40 and the microvalve X1 so that the microvalve X1 and the body portion 40 do not come into direct contact with each other. In this way, the valve fixing portion X8 can absorb the difference in the linear expansion coefficient between the micro valve X1 and the body portion 40. This is because the linear expansion coefficient of the valve fixing portion X8 is a value between the linear expansion coefficient of the microvalve X1 and the linear expansion coefficient of the body portion 40.

[Structure of micro valve X1]
Here, the configuration of the micro valve X1 will be further described. As shown in FIGS. 6 and 7, 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 the first outer layer X11, the intermediate layer X12, and the second outer layer X13 are laminated in this order. 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. 6, 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. 6, 8 and 9, 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. 9, 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. 8, 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 fixed portion X121, a first outer layer X11, and a second outer layer X13. A part of the refrigerant that has passed through the indoor evaporator 18 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 as a whole. The electrical wirings X6 and X7 are electrical wirings for changing and displacing the temperatures of the plurality of first ribs X123 and the plurality of second ribs X124.

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

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 the 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 as to approach the spine X125 side from the first fixing portion X121 side so as to be offset toward the beam X127 side in the longitudinal direction of the spine X125. .. The plurality of first ribs X123 extend in parallel with 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 the 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 as to be 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 portion 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 fixing 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 with each other via the fluid chamber X19 when it is in a certain position, and when it is in another position, it is the first. 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 the 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 electric 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. 6 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 microvalve 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 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 power 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. 13 and 14. 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. 10 and 11, 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 microvalve X1 from one surface of the microvalve X1, passes through the microvalve X1, and flows out of the microvalve X1 from the same side surface of the microvalve 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 inside of 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 decrease in temperature, 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 changes their postures integrally with the hinge XP0 as the fulcrum and the connection position XP2 as the power 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. 8 and 9. Hereinafter, this position of the movable portion X128 is referred to as a non-energized position.

As shown in FIGS. 8 and 9, 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.

In the evaporation pressure adjusting valve 19 configured as described above, as shown in FIG. 12, the evaporation pressure adjusting valve 19 is opened when the micro valve X1 is energized, and the outer pressure chamber 440b and the communication passage 430 are connected to each other. It becomes a communication state. As a result, the main valve body 45 is displaced to a position where the load acting on the axial DRa is balanced with respect to itself. That is, the evaporation pressure adjusting valve 19 is in the adjusted state shown in FIG.

Further, as shown in FIG. 12, the evaporation pressure adjusting valve 19 is in a closed state when the micro valve X1 is not energized, and the outer pressure chamber 440b and the communication passage 430 are in a non-communication state. As a result, the main valve body 45 is displaced to the position where the throttle opening degree of the evaporation pressure adjusting valve 19 is maximized. That is, the evaporation pressure adjusting valve 19 is in the fully open state shown in FIG. As described above, the micro valve X1 constitutes a valve component for adjusting the throttle opening degree of the evaporation pressure adjusting valve 19.

The control device 100 stops energization of the micro valve X1 so that the evaporation pressure adjusting valve 19 is fully opened in the cooling mode and the heating mode. Further, the control device 100 energizes the micro valve X1 so that the evaporation pressure adjusting valve 19 is in the adjusted state in the dehumidifying / heating mode.

The refrigeration cycle device 10 described above can switch the evaporation pressure adjusting valve 19 from the adjusted state to the fully open state by the valve module X0 which is a function switching unit. Therefore, for example, when it is necessary to increase the endothermic capacity of the indoor evaporator 18 on the upstream side of the evaporation pressure adjusting valve 19, by switching the evaporation pressure adjusting valve 19 to the fully open state, the endothermic effect of the indoor evaporator 18 can be obtained. It can be exerted properly. Specifically, since the refrigeration cycle device 10 switches the evaporation pressure adjusting valve 19 to the fully open state in the cooling mode, the endothermic effect of the indoor evaporator 18 can be appropriately exerted.

In addition, since the evaporation pressure adjusting valve 19 is configured to adjust the throttle opening degree by using the micro valve X1, it can be easily miniaturized as compared with the case where an electromagnetic valve or an electric valve is 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 the miniaturization as compared with the solenoid valve and the electric valve that do not use such a lever.

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 caused by heat, the noise reduction effect is high.

As described above, the valve casing X2 is made of a resin material having a linear expansion coefficient having a value between the linear expansion coefficient of the microvalve X1 and the linear expansion coefficient of the passage forming portion 44. As a result, the valve casing X2 can absorb the difference in the linear expansion coefficient between the micro valve X1 and the passage forming portion 44. That is, since the stress of thermal strain due to the temperature change of the passage forming portion 44 is absorbed by the valve casing X2, the microvalve X1 can be protected.

Further, the valve fixing portion X8 is made of a resin material having a linear expansion coefficient having a value between the linear expansion coefficient of the microvalve X1 and the linear expansion coefficient of the body portion 40. As a result, the valve fixing portion X8 can absorb the difference in the linear expansion coefficient between the micro valve X1 and the body portion 40. That is, since the stress of thermal strain due to the temperature change of the body portion 40 is absorbed by the valve fixing portion X8, the microvalve 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 passage forming portion 44. That is, the depth of the recess formed in the passage forming portion 44 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 refrigerant inlet is on the surface of the valve module X0 on the passage forming portion 44 side, and the refrigerant outlet is on the opposite surface of the valve module X0. Suppose there was. In that case, it is necessary to form refrigerant flow paths on both sides of the valve module X0. Therefore, when trying to accommodate the refrigerant flow paths on both sides of the valve module X0 in the passage forming portion 44, the dent that must be formed in the passage forming portion 44 in order to arrange the valve module X0 becomes deep. Further, since the micro valve X1 itself is small, it is possible to further reduce the digging of the passage forming portion 44.

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 hole X16 and the second refrigerant hole X17 are formed, the electrical wirings X6 and X7 are placed in the atmosphere. Can be placed closer to the atmosphere. Therefore, a sealing 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 evaporative pressure adjusting valve 19 can be downsized.

Further, since the micro valve X1 is lightweight, the evaporative pressure adjusting valve 19 is reduced in weight. Since the power consumption of the micro valve X1 is small, the power consumption of the evaporation pressure adjusting valve 19 is reduced.

(Variation example of the first embodiment)
In the above-mentioned first embodiment, as the refrigerant circuit in the dehumidifying / heating mode, the outdoor heat exchanger 16 and the indoor evaporator 18 are connected in parallel, but the present invention is not limited thereto. For example, in the refrigerant circuit in the cooling mode, if the cold air bypass passage 35 is blocked by the air mix door 34, the blown air dehumidified by the indoor evaporator 18 can be heated by the indoor condenser 12 and blown out into the vehicle interior. .. That is, dehumidification and heating in the vehicle interior can be realized even in the refrigerant circuit in the cooling mode. Therefore, the refrigeration cycle device 10 may be configured to be switchable to a series dehumidification / heating mode realized by a refrigerant circuit in which the outdoor heat exchanger 16 and the indoor evaporator 18 are connected in series.

In the series dehumidifying / heating mode, the evaporation pressure adjusting valve 19 is fully opened in order to prevent the evaporation pressure adjusting valve 19 from unintentionally operating to the closed side. That is, as shown in FIG. 13, the control device 100 controls the valve module X0 so that the outer pressure chamber 440b and the communication passage 430 are in a non-communication state (that is, a closed state) in the series dehumidification / heating mode.

(Second Embodiment)
Next, the second embodiment will be described with reference to FIGS. 14 and 15. In this embodiment, an example in which the evaporation pressure adjusting valve 19 described in the first embodiment is applied to the refrigerating cycle device Z10 constituting the cooling device Z1 of the in-vehicle device will be described. 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.

The cooling device Z1 shown in FIG. 14 is a device in which the air supplied to the vehicle interior and the battery BT are targeted for cooling of the refrigerating cycle device Z10, and the air supplied to the vehicle interior and the battery BT are adjusted to desired temperatures.

As shown in FIG. 14, the refrigerating cycle device Z10 includes a compressor Z11, a radiator Z12, a cooling pressure reducing unit Z14, a cooling evaporator Z15, a battery decompression unit Z16, a battery evaporator Z17, and an evaporation pressure adjusting valve. It is equipped with 19. Each of these constituent devices is connected to each other by a refrigerant pipe. Further, the refrigeration cycle device Z10 includes a control device Z100 that controls the operation of each component device.

The compressor Z11 sucks in the refrigerant, compresses it, and discharges it in the refrigerating cycle device Z10. The compressor 11 is composed of an electric compressor, and its operation is controlled by a control signal output from the control device 100.

The refrigerant inlet side of the radiator Z12 is connected to the refrigerant discharge side of the compressor Z11. The radiator Z12 is a heat exchanger that dissipates heat from the refrigerant discharged from the compressor Z11. Specifically, the radiator Z12 includes a refrigerant flow path portion Z121 through which the refrigerant flows and a heat medium flow path portion Z122 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 radiating the heat medium to the air blown into the vehicle interior, a radiator for radiating the heat medium to the battery BT, and the like.

A cooling pressure reducing unit Z14 is connected to the refrigerant outlet side of the radiator Z12. The cooling decompression unit Z14 is a decompression unit that decompresses the refrigerant that has passed through the radiator Z12 during air conditioning in the vehicle interior. The cooling pressure reducing unit Z14 is composed of a variable throttle with a fully closed function.

The refrigerant inlet side of the cooling evaporator Z15 is connected to the refrigerant outlet side of the cooling decompression unit Z14. The cooling evaporator Z15 heat-exchanges the refrigerant decompressed by the cooling decompression unit Z14 with the air blown from the indoor blower Z151 to evaporate the refrigerant. That is, the cooling evaporator Z15 is a cooler that cools the air blown from the indoor blower Z151 by exchanging heat with the refrigerant. The indoor blower 151 is a blower that blows air cooled by the cooling evaporator Z15 into the vehicle interior.

An evaporation pressure adjusting valve 19 is connected to the refrigerant outlet side of the cooling evaporator Z15. The evaporation pressure adjusting valve 19 functions to adjust the refrigerant evaporation pressure in the cooling evaporator Z15 to a reference pressure higher than a reference pressure capable of suppressing frost formation in order to suppress frost formation in the cooling evaporator Z15. The evaporation pressure adjusting valve 19 has the same configuration as that described in the first embodiment.

Here, the battery decompression section Z16 is connected to the refrigeration cycle device Z10 on the refrigerant outlet side of the radiator Z12 so as to be in parallel with the cooling decompression section Z14. Specifically, a branch portion Z21 is provided between the radiator Z12 and the cooling pressure reducing portion Z14. The branch portion Z21 is for allowing a part of the refrigerant flowing from the radiator Z12 toward the cooling decompression unit Z14 to flow toward the battery decompression unit Z16.

Further, a battery decompression unit Z16 is connected to the downstream side of the refrigerant flow of the branch portion Z21. The battery decompression unit Z16 is a decompression unit that decompresses the refrigerant flowing in through the branch portion Z21 when the battery BT is cooled. The battery decompression unit Z16 is composed of a variable diaphragm with a fully closed function.

The refrigerant inlet side of the battery evaporator Z17 is connected to the refrigerant outlet side of the battery decompression unit Z16. The battery evaporator Z17 is an evaporator that evaporates the refrigerant decompressed by the battery decompression unit Z16. The battery evaporator Z17 is a heat absorber that absorbs heat from the battery BT to evaporate the refrigerant. In other words, the battery evaporator Z17 is a battery cooler that cools the battery BT by heat exchange with the refrigerant.

On the downstream side of each refrigerant flow of the evaporation pressure adjusting valve 19 and the battery evaporator Z17, a merging portion Z23 for merging the refrigerant passing through the evaporation pressure adjusting valve 19 and the refrigerant passing through the battery evaporator Z17 is provided. There is. The downstream side of the refrigerant flow of the merging portion Z23 is connected to the refrigerant suction side of the compressor Z11.

The control device Z100 of the cooling device Z1 is composed of a microcomputer including a memory such as a processor, a ROM, and a RAM, and peripheral circuits thereof, similarly to the control device 100 of the first embodiment. The memory of the control device Z100 is composed of a non-transitional substantive storage medium.

An air conditioning sensor Z101 and a battery sensor Z102 are connected to the input side of the control device Z100. The air conditioning sensor Z101 is composed of a plurality of types of sensors used for controlling the cooling process. Further, the battery sensor Z102 is composed of a plurality of types of sensors used for controlling the cooling process of the battery BT. The battery sensor Z102 includes, for example, a temperature sensor that detects the battery temperature of the battery BT.

The control device Z100 can switch the operation mode to a cooling mode for cooling the vehicle interior, a battery cooling mode for cooling the battery BT, and a cooling cooling mode for cooling the vehicle interior and cooling the battery BT.

The control device Z100 switches the operation mode to any one of a cooling mode, a battery cooling mode, and a cooling cooling mode according to the information acquired by, for example, the air conditioning sensor Z101 and the battery sensor Z102. Hereinafter, the cooling mode, the battery cooling mode, and the cooling cooling mode will be described.

(A) When the operation mode is set to the cooling mode, the cooling mode control device Z100 switches to a refrigerant circuit in which the entire amount of the refrigerant that has passed through the radiator Z12 flows through the cooling evaporator Z15. That is, the control device 100 controls the battery decompression unit Z16 so as to be in the fully closed state, and controls the cooling decompression unit Z14 so as to have a throttle opening that exerts a decompression action instead of the fully closed state. Further, as shown in FIG. 15, the control device Z100 controls the evaporation pressure adjusting valve 19 to the fully open state.

In the configuration of this refrigerant circuit, the high-pressure refrigerant discharged from the compressor Z11 is radiated to the heat medium by the radiator Z12, then flows into the cooling decompression unit Z14, and is decompressed and expanded until it becomes a low-pressure refrigerant. Then, the low-pressure refrigerant decompressed by the cooling decompression unit Z14 flows into the cooling evaporator Z15, absorbs heat from the blown air blown from the indoor blower Z151, and evaporates. As a result, the blown air is cooled. The refrigerant flowing out of the cooling evaporator Z15 passes through the evaporation pressure adjusting valve 19, is sucked from the suction side of the compressor Z11, and is compressed again by the compressor Z11.

As described above, in the cooling mode, cooling of the vehicle interior can be realized by cooling the blown air by the endothermic action of the indoor evaporator 18. In particular, since the evaporation pressure adjusting valve 19 is in the fully open state in the cooling mode of the present embodiment, the endothermic effect of the indoor evaporator 18 is more appropriate than in the case where the evaporation pressure adjusting valve 19 is in the adjusted state. Can be demonstrated.

(B) Battery cooling mode When the operation mode is set to the battery cooling mode, the battery cooling mode control device Z100 switches to a refrigerant circuit in which the entire amount of the refrigerant that has passed through the radiator Z12 flows through the battery evaporator Z17. That is, the control device 100 controls the cooling decompression unit Z14 so as to be in the fully closed state, and controls the battery decompression unit Z16 so as to have a throttle opening that exerts a depressurizing action instead of being in the fully closed state. Further, as shown in FIG. 15, the control device Z100 controls the evaporation pressure adjusting valve 19 to the fully open state. In the battery cooling mode, since the refrigerant does not flow into the cooling evaporator Z15, the evaporation pressure adjusting valve 19 may be controlled in the adjusted state by the control device 100.

In the configuration of this refrigerant circuit, the high-pressure refrigerant discharged from the compressor Z11 is radiated to the heat medium by the radiator Z12, then flows into the battery decompression unit Z16, and is decompressed and expanded until it becomes a low-pressure refrigerant. Then, the low-pressure refrigerant decompressed by the battery decompression unit Z16 flows into the battery evaporator Z17, absorbs heat from the battery BT, and evaporates. As a result, the battery BT is cooled. The refrigerant flowing out of the battery evaporator Z17 is sucked from the suction side of the compressor Z11 and compressed again by the compressor Z11.

As described above, in the battery cooling mode, the battery BT can be cooled by the endothermic action of the battery evaporator Z17.

(C) Cooling / Cooling Mode When the operation mode is set to the cooling / cooling mode, the cooling / cooling mode control device Z100 switches to a refrigerant circuit in which the refrigerant that has passed through the radiator Z12 flows to the cooling evaporator Z15 and the battery evaporator Z17. That is, the control device Z100 controls the cooling decompression unit Z14 and the battery decompression unit Z16 so as to have a throttle opening that exerts a depressurizing action. Further, as shown in FIG. 15, the control device Z100 controls the evaporation pressure adjusting valve 19 to the adjusted state.

In this refrigerant circuit configuration, the high-pressure refrigerant discharged from the compressor Z11 is radiated to the heat medium by the radiator Z12, and then flows into each of the cooling decompression section Z14 and the battery decompression section Z16 to become a low-pressure refrigerant. It is expanded under reduced pressure.
Then, the low-pressure refrigerant decompressed by the cooling decompression unit Z14 flows into the cooling evaporator Z15, absorbs heat from the blown air blown from the indoor blower Z151, and evaporates. Further, the low-pressure refrigerant decompressed by the battery decompression unit Z16 flows into the battery evaporator Z17, absorbs heat from the battery BT, and evaporates. As a result, the blown air is cooled and the battery BT is cooled.

The refrigerant that has passed through the cooling evaporator Z15 merges with the refrigerant that has flowed out from the battery evaporator Z17 after passing through the evaporation pressure adjusting valve 19, and is sucked into the suction side of the compressor Z11.

As described above, in the cooling cooling mode, the battery BT can be cooled by the endothermic action of the battery evaporator Z17 while cooling the blown air by the endothermic action of the indoor evaporator 18.

Here, in the cooling cooling mode, the evaporation pressure adjusting valve 19 is in the adjusted state, and the refrigerant pressure of the cooling evaporator Z15 is adjusted to be equal to or higher than the reference pressure. Therefore, even if the cooling evaporator Z15 and the battery evaporator Z17 are connected in parallel, the refrigerant pressure in the battery evaporator Z17 may be lower than the refrigerant pressure in the cooling evaporator Z15. can.

The cooling device Z1 described above includes an evaporation pressure adjusting valve 19 in which the refrigerating cycle device Z10 can switch between an adjusted state and a fully open state. Therefore, by switching the evaporation pressure adjusting valve 19 between the adjusted state and the fully open state according to the operation mode of the refrigerating cycle device 10, the endothermic action of the evaporator used among the cooling evaporator Z15 and the battery evaporator Z17 can be obtained. It can be exerted properly. It should be noted that the action and effect obtained by the evaporative pressure adjusting valve 19 including the micro valve X1 can be obtained in the same manner as in the first embodiment.

(Modified example of the second embodiment)
In the second embodiment described above, the example in which the evaporation pressure adjusting valve 19 is connected to the refrigerant outlet side of the cooling evaporator Z15 is exemplified, but the present invention is not limited to this. The evaporation pressure adjusting valve 19 may be connected to, for example, the refrigerant outlet side of the battery evaporator Z17. In this case, in the cooling cooling mode, the refrigerant pressure in the cooling evaporator Z15 can be made lower than the refrigerant pressure in the battery evaporator Z17.

(Third Embodiment)
Next, the third embodiment will be described. In this embodiment, the microvalve 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 microvalve X1 includes a failure detection unit X50 for detecting a failure of the microvalve X1 as shown in FIGS. 16 and 17.

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 piezo resistance type strain sensor. The failure detection unit X50 may be connected to the arm X126 via an electrical insulating film so as not to conduct with 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 vehicle air conditioner 1. Alternatively, the external control device X55 may be a meter ECU that displays the vehicle speed, the remaining fuel amount, the remaining battery amount, 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 strain amount of the arm X126. On the other hand, if the microvalve X1 is normal, there is also a correlation between the amount of electricity supplied from the electrical wirings X6 and X7 to the microvalve X1 and the position of the movable portion X128. This energization 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 microvalve 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 a predetermined second map, the power supplied from the electric wirings X6 and X7 required to realize the position in the normal state to the microvalve 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 voltage signal level and the position in the first map may be determined in advance by an experiment or the like. Further, the correspondence relationship between the position in the second map and the supplied power 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 microvalve 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 a failure has occurred in the micro valve X1. 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 microvalve 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, when the external control device X55 determines that the micro valve X1 is out of order, the external control device X55 performs energization stop control. In the energization stop control, the external control device X55 stops the energization from the electric wirings X6 and X7 to the microvalve 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 microvalve X1 is operating normally, so that the external control device X55 determines the presence or absence of a failure of the microvalve X1. 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 whether or not the microvalve X1 has failed based on the relationship between the amount of electricity supplied from the electrical wirings X6 and X7 to the microvalve 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, instead of the bridge circuit, a plurality of electrodes forming a capacitive component are formed on the arm X126. 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 the 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 embodiment, the microvalve X1 of the valve module X0 is exemplified by a normally closed valve, but the present invention is not limited thereto. The micro valve X1 may be configured as a normally open valve.

As in the above-described embodiment, it is desirable, but not limited to, the evaporative pressure adjusting valve 19 to have a valve casing X2 or the like interposed between the micro valve X1 and the passage forming portion 44. The evaporative pressure adjusting valve 19 may be configured such that, for example, the micro valve X1 and the passage forming portion 44 or the like are in contact with each other without passing through the valve casing X2 or the like. Further, the valve casing X2 is not limited to the resin. Further, an additional member capable of absorbing the difference in linear expansion coefficient may be interposed between the valve casing X2 and the passage forming portion 44.

In the above-described embodiment, a plurality of first ribs X123 and a plurality of second ribs X124 are energized to generate heat, and the heat generated causes the temperature to rise to expand. However, these members may be made of a shape memory material whose length changes as the temperature changes.

In the above-described embodiment, an example in which the refrigerating cycle device 10 of the present disclosure is applied to the vehicle air-conditioning device 1 and the cooling device Z1 has been described, but the present invention is not limited thereto. The refrigeration cycle device 10 can be widely applied to devices other than the vehicle air conditioner 1 and the cooling device Z1.

Needless to say, in the above-described embodiment, the elements constituting the embodiment are not necessarily essential except when it is clearly indicated 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, quantity, range, etc. of the components of the embodiment are mentioned, when it is clearly indicated that it is particularly essential, and when it is clearly limited to a specific number in principle. Except for cases, etc., it is not limited to the specific number.

In the above-described embodiment, when the shape, positional relationship, etc. of a component or the like is referred to, the shape, positional relationship, etc. are not specified unless otherwise specified or limited in principle 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.

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 configured by 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 part or all of the above embodiments, the refrigeration cycle apparatus comprises a compressor, a radiator, a plurality of pressure reducing parts, a plurality of evaporators, and an evaporation pressure regulating valve. And. The evaporative pressure adjusting valve switches between an adjusted state in which the throttle opening is adjusted according to the refrigerant pressure of some evaporators and a fully open state in which the throttle opening is fully opened regardless of the refrigerant pressure of some evaporators. Includes a function switching unit. The function switching unit includes a valve component for adjusting the throttle opening. In the valve component, the base 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 a fulcrum, the amplification unit with the urging position urged by the drive unit as the force point, and the connection position between the amplification unit and the movable unit as the point of action. ing.

According to the second aspect, the function switching unit includes a component mounting portion for mounting the valve component on the object to be mounted to which the valve component is to be 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.

According to this, 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 third aspect, 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. ..

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 fourth aspect, the refrigerating cycle device includes a control device for controlling the operation of the function switching unit. The control device controls the function switching unit so that the evaporation pressure adjusting valve is in the adjusted state in the operation mode in which the endothermic action is exerted in each of some evaporators and other evaporators other than some evaporators. Further, the control device controls the function switching unit so that the evaporation pressure adjusting valve is fully opened in the operation mode in which some evaporators exert an endothermic action and other evaporators do not exert an endothermic action. As described above, when the endothermic action is exhibited in some evaporators, the endothermic effect of the evaporators can be appropriately exerted by switching the evaporation pressure adjusting valve to the fully open state.

According to the fifth aspect, the valve component includes a failure detection unit that outputs a signal for determining whether the valve component is operating normally or failing. By outputting such a signal from the valve component, it is possible to easily determine whether or not the valve component has failed.

According to the sixth aspect, the signal 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 seventh 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 eighth aspect, the failure detection unit outputs a signal to a device that activates 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 ninth aspect, the valve component is composed of a semiconductor chip. According to this, the valve component can be configured in a small size.

According to the tenth aspect, the evaporative pressure adjusting valve includes a body portion, a passage forming member, a main valve body, an elastic member, and a function switching portion. The function switching unit includes a valve component for adjusting the pressure difference between the first pressure chamber and the second pressure chamber. The valve component is configured in the same manner as described in the first aspect.

11 Compressor 12 Indoor condenser (heat sink)
15a 1st expansion valve 15b 2nd expansion valve 16 Outdoor heat exchanger 18 Indoor evaporator 19 Evaporation pressure control valve X0 Valve module (function switching unit)
X1 micro valve (valve parts)

Claims (10)

It ’s a refrigeration cycle device.
Compressors (11, Z11) that compress and discharge the refrigerant, and
A radiator (12, Z12) that dissipates heat from the refrigerant discharged from the compressor, and
A plurality of decompression units (15a, 15b, Z14, Z16) connected so as to be parallel to each other on the downstream side of the refrigerant flow of the radiator.
A plurality of evaporators (16, 18, Z15, Z17) connected to the downstream side of the refrigerant flow of each of the plurality of decompression sections and evaporating the decompressed refrigerant in the decompression section.
A evaporation pressure adjusting valve (19), which is connected to the refrigerant outlet side of some of the plurality of evaporators and maintains the refrigerant pressure of some of the evaporators at a predetermined value or higher, is provided.
The evaporative pressure adjusting valve is fully open so that the throttle opening is fully opened regardless of the adjustment state in which the throttle opening is adjusted according to the refrigerant pressure of some of the evaporators and the refrigerant pressure of some of the evaporators. Includes a function switching unit (X0) to switch to the state,
The function switching unit (X0) includes a valve component (X1) for adjusting the throttle opening degree.
The valve parts are
A base (X11, X12, X13) forming a fluid chamber (X19) through which at least a part of the refrigerant that has passed through the partial evaporator flows.
The drive unit (X123, X124, X125) that displaces when its own temperature changes,
An amplification unit (X126, X127) that amplifies the displacement due to a change in the temperature of the drive unit, and
It has a movable part (X128) that adjusts the flow rate 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 urges 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. The amplification unit urges the movable portion at the connection position (XP3) 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 function switching unit includes a component mounting portion (X3, X8) for mounting the valve component on an object to be mounted (40, 44) to which the valve component is mounted.
The refrigerating cycle apparatus according to claim 1, 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. 2. 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 described in. A control device (100) for controlling the operation of the function switching unit is provided.
The control device is
In the operation mode in which the endothermic action is exerted in each of the partial evaporator and the other evaporators other than the partial evaporator, the function switching unit is controlled so that the evaporation pressure adjusting valve is in the adjusted state. ,
A claim for controlling the function switching unit so that the evaporation pressure adjusting valve is in the fully open state in an operation mode in which the endothermic action is exerted by some of the evaporators and the endothermic action is not exerted by the other evaporators. Item 6. The refrigerating cycle apparatus according to any one of Items 1 to 3. The valve component is provided with a failure detection unit (X50) for outputting a signal for determining whether the valve component is operating normally or failing, according to any one of claims 1 to 4. The refrigeration cycle device described. The refrigeration cycle apparatus according to claim 5, wherein the signal is a signal corresponding to the amount of strain of the amplification unit. The drive unit generates heat when energized and generates heat.
The refrigeration cycle device according to claim 5 or 6, wherein the failure detection unit outputs the signal to a device (X55) that stops energization of the valve component when the valve component is out of order. 6. Refrigeration cycle equipment. The refrigeration cycle apparatus according to any one of claims 1 to 8, wherein the valve component is composed of a semiconductor chip. An evaporation pressure adjusting valve for maintaining the refrigerant pressure of the evaporator (18) constituting the refrigerating cycle apparatus (10) above a predetermined value.
Refrigerant inflow path (41) into which the refrigerant that has passed through the evaporator flows in, a valve chamber (43) in which the refrigerant flows from the refrigerant inflow path, and the refrigerant flows out from the valve chamber to the refrigerant suction side of the compressor (11). The body portion (40) in which the refrigerant outflow path (42) is formed, and
A passage forming member (44) arranged in the valve chamber to form a communication passage (430) for communicating the refrigerant inflow passage and the refrigerant outflow passage, and to form a cylinder chamber (440) inside the communication passage. When,
A main valve body (45) that is slidably arranged with respect to the cylinder chamber and that adjusts the throttle opening of the communication passage by receiving the refrigerant pressure in the refrigerant inflow passage.
An elastic member (46) that applies an urging force to the main valve body so as to oppose the refrigerant pressure in the refrigerant inflow path acting on the main valve body.
A function switching unit (X0) that switches between an adjusted state in which the throttle opening is adjusted according to the refrigerant pressure of the evaporator and a fully open state in which the throttle opening is fully opened regardless of the refrigerant pressure of the evaporator. Equipped with
The cylinder chamber is divided by the main valve body into a first pressure chamber (440a) communicating with the refrigerant inflow passage and a second pressure chamber (440b) communicating with the refrigerant outflow passage.
The first pressure chamber and the second pressure chamber communicate with each other via a pressure equalizing passage (451a).
The main valve body is arranged in the cylinder chamber so as to be displaced according to the pressure difference between the first pressure chamber and the second pressure chamber.
The function switching unit includes a valve component (X1) for adjusting the pressure difference between the first pressure chamber and the second pressure chamber.
The valve parts are
A fluid chamber (X19) through which a refrigerant flows, a first fluid hole (X16) that communicates the second pressure chamber and the fluid chamber, and a second fluid hole (X17) that communicates the fluid chamber and the refrigerant outflow passage. The base (X11, X12, X13) on which the
The drive unit (X123, X124, X125) that displaces when its own temperature changes,
An amplification unit (X126, X127) that amplifies the displacement due to a change in the temperature of the drive unit, and
It has a movable portion (X128) that adjusts the opening degree of the second fluid hole in the fluid chamber by transmitting and moving the displacement amplified by the amplification portion.
When the drive unit is displaced due to a change in temperature, the drive unit urges 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. The amplification unit urges the movable portion at the connection position (XP3) between the amplification unit and the movable portion.
An evaporative pressure regulating valve in which the distance from the hinge to the connection position is longer than the distance from the hinge to the urging position.

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