JP2012082908A - Stacked valve - Google Patents

Abstract

PROBLEM TO BE SOLVED: To easily and inexpensively manufacture a stacked valve including a plurality of control valves.SOLUTION: Switching valves 41 and 42 include the plurality of control valves for controlling the flow of working fluid. The switching valves 41 and 42 include a common body 105 and path forming members 126 and 128. The common body 105 has an internal space formed to house the valve parts of the plurality of control valves, and includes an insertion port for inserting the valve parts, an introduction port 120 for introducing the working fluid, and leading-out ports 122 and 124 for leading out the working fluid. The path forming members 126 and 128 are inserted into the body 105 through the insertion port and form refrigerant paths for connecting the introduction port 120 to the leading-out ports 122 and 124. The insertion port of the body 105 is sealed by a solenoid 104.

Description

  The present invention relates to a collective valve including a plurality of control valves that control the flow of a working fluid.

  An automobile air conditioner is generally configured by arranging a compressor, a condenser, an evaporator, and the like in a refrigerant circulation passage. Various control valves are provided for switching the refrigerant circulation passage and adjusting the refrigerant flow rate according to the operating state of the refrigeration cycle (see, for example, Patent Document 1). As such a control valve, there is a mechanical valve whose valve part is opened and closed by a balance between the force due to the pressure received from the refrigerant and the biasing force of the spring against it, and an actuator for electrically adjusting the opening degree from the outside. The electrically driven valve provided is used as appropriate.

JP-A-11-287354

  By the way, when various control valves are provided in such an air conditioner, it may be preferable to configure a plurality of control valves as a collective valve from the viewpoint of saving space and reducing material costs. However, when constructing such a collective valve, control valves of various sizes must be incorporated in a common body, and the body may become unnecessarily large depending on the assembly mode. In addition, the shape of the internal passage is complicated due to the size and positional relationship of the valve portions of the control valves, and it may be difficult to form the passage to the body itself.

  One of the objects of the present invention is to enable a collective valve including a plurality of control valves to be manufactured easily and at low cost.

  The collective valve of an aspect of the present invention includes a plurality of control valves that control the flow of the working fluid. This collective valve is formed with an internal space for accommodating the valve portions of a plurality of control valves, an insertion port for inserting the valve portion, an introduction port for introducing the working fluid, and a working fluid is led out. And a passage forming member that is inserted into the body through an insertion port and that defines a refrigerant passage that connects the introduction port and the outlet port. The body insertion port is sealed by a part of any of the plurality of control valves.

  According to this aspect, a plurality of control valves are assembled in a common body, but since the passage forming member is assembled in the body in a separately manufactured state, it is not necessary to perform complicated processing on the body itself for forming the passage. . That is, for the shared body, simple processing for forming the internal space and the insertion port, introduction port, and lead-out port connected to the internal space may be performed, and a separately formed passage forming member is incorporated from the insertion port. An internal passage having a desired shape can be formed by a simple method. In addition, the shared body has restrictions on the connection structure with external piping, etc., but the shape and dimensions of the passage forming member can be set independently of the body, so the design flexibility as a collective valve is reduced. improves. Furthermore, since the insertion port of the body is sealed by a part of any of the plurality of control valves, and the control valve also serves as a lid of the body, the design is efficient with little waste. In particular, when an electric drive valve having an electric drive unit is included as a control valve, the drive unit generally tends to be large. Therefore, if the drive part is exposed to the outside of the body, the body can be made compact and the insertion port can be sealed, so that the material cost can be reduced and the entire collecting valve can be made compact. become.

  According to the present invention, the collecting valve can be manufactured easily and at low cost.

1 is a system configuration diagram illustrating a schematic configuration of a vehicle air conditioning apparatus according to a first embodiment. It is explanatory drawing showing operation | movement of the vehicle air conditioner. It is sectional drawing showing the specific structure of a switching valve. It is a system block diagram showing schematic structure of the vehicle air conditioner which concerns on 2nd Embodiment. It is explanatory drawing showing operation | movement of the vehicle air conditioner. It is sectional drawing showing the specific structure of a 2nd control valve unit.

Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings.
[First Embodiment]
First, a first embodiment of the present invention will be described. FIG. 1 is a system configuration diagram illustrating a schematic configuration of the vehicle air conditioning apparatus according to the first embodiment. In the present embodiment, the vehicle air conditioning apparatus including the collective valve of the present invention is embodied as an electric vehicle air conditioning apparatus.

  The vehicle air conditioner 1 includes a refrigeration cycle (refrigerant circuit) in which a compressor 2, an indoor condenser 3, an outdoor heat exchanger 5, a liquid tank 6, an evaporator 7 and an accumulator 8 are connected by piping. The vehicle air conditioner 1 is a heat pump type air conditioner that performs air conditioning in the vehicle interior using the heat of the refrigerant in a process in which alternative refrigerant (HFC-134a) as a refrigerant circulates while changing its state in the refrigeration cycle. It is configured as. Various control valves for appropriately controlling the cooling and heating are disposed in the refrigerant circulation circuit.

  The vehicle air conditioner 1 is operated so as to switch a plurality of refrigerant circulation passages between a cooling operation and a heating operation. The refrigeration cycle is configured so that the indoor condenser 3 and the outdoor heat exchanger 5 can be operated in series as a condenser, and the evaporator 7 and the outdoor heat exchanger 5 can be operated as an evaporator, respectively. It is configured. That is, the first refrigerant circulation passage through which refrigerant circulates during cooling operation (dehumidification), the second refrigerant circulation passage through which refrigerant circulates during heating operation, and the refrigerant circulates during dehumidification during heating operation (specific heating operation) A third refrigerant circulation passage is formed.

  The first refrigerant circulation passage is a passage through which the refrigerant circulates in the following manner: compressor 2 → indoor condenser 3 → outdoor heat exchanger 5 → liquid tank 6 → evaporator 7 → accumulator 8 → compressor 2. The second refrigerant circulation passage is a passage through which the refrigerant circulates, such as the compressor 2 → the indoor condenser 3 → the outdoor heat exchanger 5 → the liquid tank 6 → the accumulator 8 → the compressor 2. The third refrigerant circulation passage is a passage through which the refrigerant circulates as follows: compressor 2 → indoor condenser 3 → liquid tank 6 → evaporator 7 → accumulator 8 → compressor 2. The flow of the refrigerant flowing through the outdoor heat exchanger 5 is in the same direction in the first refrigerant circulation passage and the second refrigerant circulation passage.

  Specifically, the discharge chamber of the compressor 2 is connected to the inlet of the indoor condenser 3 via the first passage 21, and the outlet of the indoor condenser 3 is connected to the inlet of the outdoor heat exchanger 5 via the second passage 22. It is connected to the. The outlet of the outdoor heat exchanger 5 is connected to the inlet of the evaporator 7 through the third passage 23, and the outlet of the evaporator 7 is connected to the inlet of the accumulator 8 through the fourth passage 24 (return passage). . The second passage 22 and the third passage 23 are connected by a bypass passage 25 so that the refrigerant derived from the indoor condenser 3 can be supplied to the evaporator 7 by bypassing the outdoor heat exchanger 5. Further, a branch point is provided on the downstream side of the junction point of the third passage 23 with the bypass passage 25, and a bypass passage 26 connected to the inlet of the accumulator 8 is provided.

  The first refrigerant circulation passage is configured by connecting the first passage 21, the second passage 22, the third passage 23, and the fourth passage 24. The second refrigerant circulation passage is configured by connecting the first passage 21, the second passage 22, the third passage 23, and the bypass passage 26. The third refrigerant circulation passage is configured by connecting the first passage 21, the second passage 22, the bypass passage 25, the third passage 23, and the fourth passage 24. In order to realize such switching of the refrigerant circulation passage, a switching valve 41 is provided at a branch point of the second passage 22 to the bypass passage 25, and at a branch point of the third passage 23 to the bypass passage 26. A switching valve 42 is provided. Further, on the downstream side of the switching valve 41 in the second passage 22, an on-off valve 43 and an orifice 44 are provided in parallel. A check valve 45 is provided on the downstream side of the outdoor heat exchanger 5. The liquid tank 6 is provided on the downstream side of the junction with the bypass passage 25 in the third passage 23. An expansion valve 9 is provided between the switching valve 42 and the evaporator 7.

  The vehicle air conditioner 1 has a duct 10 in which heat exchange of air is performed, and an indoor blower 12, an evaporator 7, and an indoor condenser 3 are arranged from the upstream side of the air flow direction in the duct 10. An air mix door 14 is rotatably provided on the upstream side of the indoor condenser 3, and the ratio between the air volume passing through the indoor condenser 3 and the air volume bypassing the indoor condenser 3 is adjusted. Moreover, the outdoor air blower 16 is arrange | positioned so that the outdoor heat exchanger 5 may be opposed.

  The compressor 2 is configured as an electric compressor that houses a motor and a compression mechanism in a housing, is driven by a supply current from a battery (not shown), and the discharge capacity of the refrigerant changes according to the rotational speed of the motor. As this compressor 2, various types of compressors such as a reciprocating type, a rotary type and a scroll type can be adopted. However, since the electric compressor itself is publicly known, the description thereof is omitted.

  The indoor condenser 3 is provided in the vehicle interior and functions as an auxiliary condenser that dissipates the refrigerant separately from the outdoor heat exchanger 5. That is, the high-temperature and high-pressure refrigerant discharged from the compressor 2 dissipates heat when passing through the indoor condenser 3. The air distributed according to the opening degree of the air mix door 14 undergoes heat exchange in the process of passing through the indoor condenser 3.

  The outdoor heat exchanger 5 is disposed outside the passenger compartment and functions as an outdoor condenser that radiates the refrigerant that passes through the interior during the cooling operation, and functions as an outdoor evaporator that evaporates the refrigerant that passes through the interior during the heating operation. The outdoor blower 16 is a suction type blower, and introduces outside air by rotationally driving an axial fan with a motor. The outdoor heat exchanger 5 exchanges heat between the outside air and the refrigerant.

  The liquid tank 6 is a device that separates and stores the refrigerant sent from the outdoor heat exchanger 5 by gas-liquid separation, and has a liquid phase part and a gas phase part. Then, the liquid refrigerant in the liquid phase part is led out toward the expansion valve 9. Since this liquid phase part contains lubricating oil circulating in the refrigeration cycle, the lubricating oil can be derived together with the liquid refrigerant.

  The evaporator 7 is arrange | positioned in a vehicle interior, and functions as an indoor evaporator which evaporates the refrigerant | coolant which passes the inside. That is, the refrigerant having a low temperature and a low pressure due to the passage of the control valve functioning as the expansion device evaporates when passing through the evaporator 7. The air introduced from the upstream side of the duct 10 is cooled by the latent heat of vaporization. At this time, the cooled and dehumidified air is distributed into one that passes through the indoor condenser 3 and one that bypasses the indoor condenser 3 according to the opening of the air mix door 14. The air passing through the indoor condenser 3 is heated during the passage process. The air that has passed through the indoor condenser 3 and the bypassed air are mixed on the downstream side of the indoor condenser 3, adjusted to a target temperature, and supplied to the interior of the vehicle from a blower outlet (not shown). For example, the air is blown out from a vent outlet, a foot outlet, a differential outlet, or the like toward a predetermined position in the vehicle interior.

  The accumulator 8 is a device that stores the refrigerant sent from the evaporator 7 by gas-liquid separation and has a liquid phase part and a gas phase part. For this reason, even if liquid refrigerant more than expected is derived from the upstream side, the liquid refrigerant can be stored in the liquid phase part, and the refrigerant in the gas phase part can be derived to the compressor 2. As a result, the compression operation of the compressor 2 is not hindered. On the other hand, in the present embodiment, a part of the refrigerant in the liquid phase portion can be supplied to the compressor 2, and a necessary amount of lubricating oil can be returned to the compressor 2.

  The expansion valve 9 is configured as a so-called temperature type expansion valve, detects the temperature and pressure on the outlet side of the evaporator 7, adjusts the valve opening, and supplies liquid refrigerant corresponding to the heat load to the evaporator 7. To do. Since such a temperature type expansion valve itself is publicly known, detailed description thereof is omitted.

  The switching valve 41 includes a first valve portion that opens and closes the second passage 22 (passage that connects the indoor condenser 3 and the outdoor heat exchanger 5), a second valve portion that opens and closes the bypass passage 25, and one valve portion. It consists of a three-way solenoid valve provided with a solenoid to be driven. The first valve portion allows the refrigerant to flow from the indoor condenser 3 to the outdoor heat exchanger 5 via the second passage 22 by opening the valve. The second valve portion allows the refrigerant to flow from the indoor condenser 3 to the liquid tank 6 via the bypass passage 25 by opening the valve. In the present embodiment, an on-off valve (on / off valve) that opens one of the first valve portion and the second valve portion and closes the other depending on whether the solenoid is energized is used as the switching valve 41. The actuator that drives the valve portion of the switching valve 41 may not be a solenoid, but may be an electric motor such as a stepping motor. The specific configuration of the switching valve 41 will be described later.

  The switching valve 42 drives the first valve portion that opens and closes the third passage 23 (the passage connecting the outdoor heat exchanger 5 and the evaporator 7), the second valve portion that opens and closes the bypass passage 26, and one valve portion. It consists of a three-way solenoid valve provided with a solenoid to perform. The first valve portion allows the refrigerant to flow from the outdoor heat exchanger 5 to the evaporator 7 via the third passage 23 by opening the valve. The second valve portion allows the refrigerant to flow from the outdoor heat exchanger 5 to the accumulator 8 via the bypass passage 26 by opening the valve. In the present embodiment, an on-off valve (on / off valve) that opens one of the first valve portion and the second valve portion and closes the other depending on whether the solenoid is energized is used as the switching valve 42. The actuator that drives the valve portion of the switching valve 42 may not be a solenoid, but may be an electric motor such as a stepping motor. A specific configuration of the switching valve 42 will be described later.

  The on-off valve 43 adjusts the opening degree of the main passage that connects the indoor condenser 3 and the outdoor heat exchanger 5. The on-off valve 43 includes a valve portion that opens and closes the main passage and a solenoid that drives the valve portion, and opens and closes the valve portion depending on the presence or absence of supply current. Further, a bypass passage that bypasses the main passage before and after the on-off valve 43 is provided, and an orifice 44 is provided in the bypass passage. The opening area of the orifice 44 is sufficiently smaller than the opening area when the on-off valve 43 is opened, but by providing the orifice 44 in parallel with the on-off valve 43 in this way, even when the on-off valve 43 is closed, A predetermined flow rate of refrigerant flow is allowed. The orifice 44 also functions as an expansion device.

  The check valve 45 is provided on the upstream side of the junction with the bypass passage 25 in the third passage 23. The check valve 45 is configured as a mechanical valve that prevents the refrigerant that has passed through the bypass passage 25 from flowing back to the outdoor heat exchanger 5 side.

  The vehicle air conditioner 1 configured as described above is controlled by the control unit 100. The control unit 100 includes a CPU that executes various arithmetic processes, a ROM that stores various control programs, a RAM that is used as a work area for data storage and program execution, an input / output interface, and the like. Signals from various sensors and switches (not shown) installed in the vehicle air conditioner 1 are input to the control unit 100. The control unit 100 calculates the control amount of each actuator in order to realize the room temperature set by the vehicle occupant, and outputs a control signal to the drive circuit of each actuator. The control unit 100 also performs drive control of the compressor 2, the indoor blower 12, the outdoor blower 16, and the air mix door 14 in addition to opening / closing control of electrically driven valves such as the switching valve 41, the switching valve 42, and the open / close valve 43.

  The control unit 100 determines whether each electrically driven valve is opened or closed based on predetermined external information detected by various sensors such as the temperature inside and outside the vehicle, the temperature of the air blown from the evaporator 7, and the like, and supplies current to each solenoid. Supply. As a modification, when the actuator of the electrically driven valve is configured by a stepping motor, a control pulse signal for opening / closing operation is output to the stepping motor. By such control, as shown in the figure, the compressor 2 introduces the refrigerant having the suction pressure Ps through the suction chamber, compresses the refrigerant, and discharges it as the refrigerant having the discharge pressure Pd.

  Next, operation | movement of the refrigerating cycle of this embodiment is demonstrated. FIG. 2 is an explanatory diagram illustrating the operation of the vehicle air conditioner. (A) shows the state during cooling operation, (B) shows the state during heating operation, and (C) shows the state during specific heating operation. The “specific heating operation” here is an operation state in which the function of dehumidification is particularly enhanced in the heating operation.

  The upper part of each figure shows a Mollier diagram for explaining the operation of the refrigeration cycle. The horizontal axis represents enthalpy, and the vertical axis represents various pressures. The lower part of each figure shows the operating state of the refrigeration cycle. Thick lines and arrows in the figure indicate the flow of the refrigerant, and symbols a to g correspond to those in the Mollier diagram. Further, “x” in the figure indicates that the flow of the refrigerant is blocked. The lower part of the figure corresponds to FIG. 1, but is simplified for convenience, for example, illustration of the air mix door 14 is omitted.

  As shown in FIG. 2A, during the cooling operation, the first valve portion of the switching valve 41 is opened and the second valve portion is closed. Then, the on-off valve 43 is opened. On the other hand, the first valve portion of the switching valve 42 is opened and the second valve portion is closed. For this reason, the bypass passages 25 and 26 are blocked, and the refrigerant discharged from the compressor 2 is guided to the outdoor heat exchanger 5. At this time, the outdoor heat exchanger 5 functions as an outdoor condenser.

  That is, the high-temperature and high-pressure gas refrigerant discharged from the compressor 2 is condensed through the indoor condenser 3 and the outdoor heat exchanger 5. Then, the refrigerant that has passed through the outdoor heat exchanger 5 is gas-liquid separated in the liquid tank 6, and the liquid refrigerant is adiabatically expanded by the expansion valve 9 to become a cold / low-pressure gas-liquid two-phase refrigerant, and the evaporator 7. To be introduced. The refrigerant introduced into the inlet of the evaporator 7 evaporates in the process of passing through the evaporator 7 and cools the air in the passenger compartment. In the illustrated example, the superheat degree SH is generated on the outlet side of the evaporator 7.

  As shown in FIG. 2B, during the heating operation, the first valve portion of the switching valve 41 is opened and the second valve portion is closed. Then, the on-off valve 43 is closed. On the other hand, the first valve portion of the switching valve 42 is closed and the second valve portion is opened. For this reason, the refrigerant derived from the outdoor heat exchanger 5 is guided to the accumulator 8 via the bypass passage 26. That is, since the refrigerant bypasses the evaporator 7, the evaporator 7 substantially does not function, and only the outdoor heat exchanger 5 functions as an evaporator.

  That is, the high-temperature and high-pressure gas refrigerant discharged from the compressor 2 is condensed through the indoor condenser 3 and is adiabatically expanded at the orifice 44 to become a cold / low-pressure gas-liquid two-phase refrigerant, and the outdoor heat exchanger 5. Evaporates through. The refrigerant that has passed through the outdoor heat exchanger 5 returns to the compressor 2 through the liquid tank 6, the switching valve 42, and the accumulator 8.

  As shown in FIG. 2C, during the specific heating operation, the first valve portion of the switching valve 41 is closed and the second valve portion is opened. On the other hand, the first valve portion of the switching valve 42 is opened and the second valve portion is closed. For this reason, the refrigerant led out from the indoor condenser 3 is guided to the liquid tank 6 through the bypass passage 25. That is, since the refrigerant bypasses the outdoor heat exchanger 5, the outdoor heat exchanger 5 does not substantially function.

  That is, the high-temperature and high-pressure gas refrigerant discharged from the compressor 2 is condensed by passing through the indoor condenser 3. Then, the refrigerant that has passed through the indoor condenser 3 is separated into gas and liquid in the liquid tank 6, and the liquid refrigerant is adiabatically expanded in the expansion valve 9 to become a cold / low pressure gas / liquid two-phase refrigerant in the evaporator 7. be introduced. The refrigerant introduced into the inlet of the evaporator 7 evaporates in the process of passing through the evaporator 7 and dehumidifies the air in the passenger compartment.

Next, specific configurations of the switching valve 41 and the switching valve 42 will be described. FIG. 3 is a cross-sectional view illustrating a specific configuration of the switching valve.
The switching valve of the present embodiment is configured by assembling a valve body 102 that houses a valve mechanism therein and a solenoid 104 that drives the valve mechanism. The body 105 of the valve body 102 controls the main valve 106 that controls the flow of refrigerant flowing from the upstream passage to the first downstream passage, and the flow of refrigerant flowing from the upstream passage to the second downstream passage. A sub valve 108 and a pilot valve 110 for controlling the open / closed state of the main valve 106 are incorporated.

  Here, the “upstream passage” here corresponds to the upstream passage in the second passage 22 for the switching valve 41 and the upstream passage in the third passage 23 for the switching valve 42. The “first downstream passage” corresponds to the downstream passage in the second passage 22 for the switching valve 41 and the downstream passage in the third passage 23 for the switching valve 42. The “second downstream side passage” corresponds to the bypass passage 25 for the switching valve 41 and the bypass passage 26 for the switching valve 42.

  The body 105 is configured by fitting a resin-made second body 114 into the metal-made first body 112 so as to be coaxially inserted. The 1st body 112 has the fitting hole 116 which penetrates a rectangular parallelepiped main body up and down, and the opening part of the fitting hole 116 is an insertion port of an internal valve mechanism. One side surface of the first body 112 is provided with an introduction port 120 that communicates the inside and outside of the first body 112 and communicates with the upstream passage, and a lead-out port 122 that communicates the interior and exterior with the lower portion and communicates with the second downstream passage. Is provided. On the opposite side surface of the first body 112, a lead-out port 124 is provided in the lower portion thereof so as to communicate with the inside and outside and to the first downstream passage.

  The second body 114 functions as a “passage forming member” that defines and forms an internal passage that connects the introduction port 120 and the outlet ports 122 and 124. The second body 114 is configured by fitting a first passage forming member 126 inserted into the first body 112 and a second passage forming member 128 incorporated into the first passage forming member 126. The first passage forming member 126 has a double pipe structure coaxial with the first body 112 in the upper half thereof, and the lower half serves as a housing portion for the second passage forming member 128. The inner pipe portion 130 of the double pipe structure has a main valve hole 132 formed therein, and a main valve seat 134 is formed by the open end portion. In addition, a communication hole that communicates the inside and the outside is formed on a surface of the outer tube portion 135 of the double tube structure facing the introduction port 120. An upstream pressure chamber 138 is formed between the inner tube portion 130 and the outer tube portion 135. A bottomed cylindrical main valve body 140 is disposed in the pressure chamber 138. The main valve body 140 is attached to and detached from the main valve seat 134 to open and close the main valve 106.

  The main valve body 140 is supported by a flexible diaphragm 142 that is sandwiched between the first passage forming member 126 and the solenoid 104. A plurality of legs are extended downward from the lower surface of the main valve body 140. Since the leg portion is slidably inserted into the inner tube portion 130, a stable opening / closing operation in the axial direction of the main valve body 140 is ensured. The center portion of the diaphragm 142 is fitted into the center portion of the main valve body 140, and the thick portion constitutes a part of the main valve body 140 that is attached to and detached from the main valve seat 134. The main valve body 140 divides the pressure chamber 138 into a high pressure chamber 146 and a back pressure chamber 148. The main valve body 140 is provided with an orifice 150 that allows the high pressure chamber 146 and the back pressure chamber 148 to communicate with each other. A plurality of slits 151 are provided at the upper opening edge of the main valve body 140 to communicate the inside and outside. Even if the main valve body 140 is located at the top dead center where the main valve body 140 is fully opened as shown in the figure, the back pressure chamber 148 The pressure is applied to the back portion of the diaphragm 142.

  A boss projecting toward the back pressure chamber 148 is provided at the center of the bottom of the main valve body 140, and a pilot valve seat 154 is formed by the upper end surface of the boss. A pilot valve hole 156 is formed so as to penetrate the boss portion in the axial direction. Further, a pilot valve body 160 driven by the solenoid 104 is disposed in the back pressure chamber 148. The pilot valve body 160 is attached to and detached from the pilot valve seat 154 to open and close the pilot valve 110. The pilot valve body 160 has an attachment / detachment portion 162 made of an elastic body (rubber in the present embodiment) fitted to the lower end portion of the elongated main body, and a rod portion 164 extending to the opposite side of the attachment / detachment portion 162 has a solenoid 104. It is connected to.

  A communication hole 170 that communicates the inside and the outside is formed on the surface of the lower half of the first passage forming member 126 that faces the outlet port 122. A valve seat forming portion 172 protruding in a cylindrical shape is provided inside the communication hole 170. A sub valve hole 174 is formed inside the valve seat forming portion 172, and a sub valve seat 176 is formed by the opening end portion thereof. A bottomed cylindrical subvalve body 178 is provided so as to face the subvalve seat 176. The sub-valve body 178 opens and closes the sub-valve 108 with its bottom attached to and detached from the sub-valve seat 176.

  The auxiliary valve body 178 is supported by a flexible diaphragm 180 that is sandwiched between the first passage forming member 126 and the second passage forming member 128. Since the sub valve body 178 is slidably supported along the right end opening of the second passage forming member 128, a stable opening / closing operation in the axial direction of the sub valve body 178 is secured. As shown in the drawing, the axis of the auxiliary valve body 178 forms an angle of 90 degrees with the axis of the main valve body 140. That is, the auxiliary valve body 178 opens and closes in a direction perpendicular to the opening and closing direction of the main valve body 140. The central portion of the diaphragm 180 is fitted to the bottom portion of the sub-valve body 178, and a thick portion along the bottom portion constitutes a part of the sub-valve body 178 that is attached to and detached from the sub-valve seat 176. The sub valve body 178 divides the interior of the body 105 into a high pressure chamber 146 that communicates with the introduction port 120, a low pressure chamber 182 that communicates with the derivation port 122, and a low pressure chamber 184 that communicates with the derivation port 124.

  Further, a cylindrical seal member 186 is fitted so as to straddle the connecting portion between the communication hole 170 and the outlet port 122. An O-ring for sealing is externally fitted to the joint surface with the first body 112 at the center of the first passage forming member 126, and the joint surface with the first passage forming member 126 is disposed on the outer peripheral surface of the seal member 186. An O-ring for sealing is externally fitted on. Accordingly, the refrigerant in the high pressure chamber 146 is prevented from leaking to the outlet port 122 side through the gap between the first body 112 and the first passage forming member 126. Also, a sealing O-ring is externally fitted to the joint surface with the first body 112 at the lower end of the first passage forming member 126. Further, a disk-shaped sealing member 188 is provided so as to seal the lower end opening of the first body 112.

  The second passage forming member 128 has a cylindrical main body, and is fitted so as to be inserted from a fitting hole 190 provided on the opposite side of the communication hole 170 in the lower half portion of the first passage forming member 126. Has been. A communication hole that allows the main valve hole 132 and the low pressure chamber 184 to communicate with each other is provided on the side of the second passage forming member 128. An inwardly extending spring receiving portion 192 is provided at the central portion in the axial direction of the second passage forming member 128. A spring 194 that biases the auxiliary valve body 178 in the valve closing direction is interposed between the spring receiving portion 192 and the auxiliary valve body 178.

  On the other hand, the solenoid 104 is attached so as to seal the upper end opening of the body 105. The solenoid 104 is disposed so as to face the core 200 in the axial direction within the sleeve 202, a core 200 connected to the body 105, a bottomed cylindrical sleeve 202 that accommodates the upper half of the core 200, and the like. Plunger 204, bobbin 206 fitted on sleeve 202, electromagnetic coil 208 wound around bobbin 206, and case 210 assembled to core 200 so as to cover electromagnetic coil 208 from the outside. .

  The pilot valve body 160 has a rod portion 164 passing through the core 200 and fitted into the plunger 204, and operates integrally with the plunger 204. Between the core 200 and the plunger 204, a spring 212 (corresponding to an “urging member”) that biases the pilot valve body 160 in the valve opening direction via the plunger 204 is interposed. A sealing O-ring is interposed between the case 210 and the body 105. A current-carrying harness 214 is drawn out from the electromagnetic coil 208. The plunger 204 has a cylindrical shape, and a communication path 216 is formed along the axial direction thereof. The communication path 216 communicates with a back pressure chamber 218 formed on the bottom side in the sleeve 202.

  In such a configuration, in the body 105, a passage connecting the high pressure chamber 146 and the low pressure chamber 184 via the main valve 106 constitutes a “first passage”, and the high pressure chamber 146 and the low pressure chamber 182 are connected to the sub valve 108. A passage that connects the high pressure chamber 146, the back pressure chamber 148, and the low pressure chamber 184 via the pilot valve 110 forms a “third passage”. The pressure P1 (referred to as “upstream pressure P1”) in the high pressure chamber 146 passes through the orifice 150 and becomes the intermediate pressure Pp in the back pressure chamber 148, while being reduced through the main valve 106 to be pressure P2 (“downstream”). Side pressure P2 "). The intermediate pressure Pp varies depending on the open / close state of the pilot valve 110. Further, the upstream pressure P1 is reduced through the auxiliary valve 108 to become a pressure P3 (referred to as “downstream pressure P3”).

  The switching valves 41 and 42 having the above-described configuration are manufactured by molding the first body 112 and the second body 114 individually and assembling them later. The second body 114 is configured in advance as a valve unit in which the main valve 106 and the sub valve 108 are incorporated, and is assembled to the first body 112. That is, the outer shape of the first body 112 and the lower hole of the fitting hole 116 are formed by hollow extrusion using a metal material, and then the fitting hole 116, the introduction port 120, the outlet port 122, and the outlet port 124 are formed. It is obtained by molding by cutting. On the other hand, the first passage forming member 126 and the second passage forming member 128 are obtained by injection molding a resin material.

  The spring unit 194, the auxiliary valve body 178, and the diaphragm 180 are assembled to the second passage forming member 128 formed in this manner, and the valve unit is inserted and fitted into the fitting hole 190 of the first passage forming member 126. Composed. Then, the sealing member 188 and the valve unit are assembled to the first body 112 so as to be inserted from the insertion port of the fitting hole 116. On the other hand, the pilot valve body 160, the main valve body 140, and the diaphragm 142 are assembled to the solenoid 104. Thereafter, the solenoid 104 is assembled so as to seal the insertion port of the first body 112, and the sealing member 186 is inserted into the outlet port 122 and assembled. In this way, the assembly of the switching valves 41 and 42 is completed.

  In the switching valves 41 and 42 configured as described above, when the solenoid 104 is turned off (non-energized state), the main valve 106 opens to open the first passage, while the sub valve 108 closes. And act to close the second passage. That is, since the solenoid force does not act, the pilot valve body 160 is urged in the valve opening direction by the spring 212, and the pilot valve 110 is opened. At this time, the intermediate pressure Pp in the back pressure chamber 148 and the downstream pressure P2 in the low pressure chamber 184 are substantially equal, while a predetermined differential pressure (P1-Pp) is generated between the upstream pressure P1 and the intermediate pressure Pp. Therefore, the main valve body 140 is pushed up to the fully open position as shown in the figure. However, since the top dead center of the main valve body 140 is regulated by the upper end of the main valve body 140 being locked to the core 200, the pilot valve 110 is maintained in the open state.

  On the other hand, since the main valve 106 is fully opened, the differential pressure (P1-P2) between the upstream pressure P1 and the downstream pressure P2 is small, and the sub valve body 178 is pressed against the sub valve seat 176 by the urging force of the spring 194. As a result, the auxiliary valve 108 is closed. That is, in the state where the solenoid 104 is off, the first passage connecting the introduction port 120 and the derivation port 124 is opened, while the second passage connecting the introduction port 120 and the derivation port 122 is closed.

  On the other hand, in a state where the solenoid 104 is turned on (energized state), the main valve 106 is closed to close the first passage, while the sub valve 108 is opened to open the second passage. That is, since the solenoid force acts, the pilot valve body 160 is driven in the valve closing direction against the biasing force of the spring 212, and the pilot valve 110 is closed. At this time, the intermediate pressure Pp of the back pressure chamber 148 and the upstream pressure P1 of the high pressure chamber 146 are substantially equal, while a predetermined differential pressure (Pp−P2) is generated between the intermediate pressure Pp. The body 140 is pushed down to the valve closing position. At this time, the closed state of the pilot valve 110 is also maintained.

  As a result, the upstream pressure P1 of the high pressure chamber 146 increases, the differential pressure (P1-P2) between the upstream pressure P1 and the downstream pressure P2 increases, and the subvalve body resists the biasing force of the spring 194. 178 is driven in the valve opening direction, and the auxiliary valve 108 is opened. That is, when the solenoid 104 is turned on, the first passage connecting the introduction port 120 and the derivation port 124 is closed, while the second passage connecting the introduction port 120 and the derivation port 122 is opened.

[Second Embodiment]
Next, a second embodiment of the present invention will be described. The vehicle air-conditioning apparatus according to the present embodiment is different from the first embodiment in the configuration of the refrigerant circulation passage and the type of the control valve, but also has portions common to the first embodiment. For this reason, about the component similar to 1st Embodiment, the same code | symbol is attached | subjected etc., and the description is abbreviate | omitted suitably. FIG. 4 is a system configuration diagram illustrating a schematic configuration of the vehicle air conditioning apparatus according to the second embodiment.

  The vehicle air conditioner 201 of the present embodiment includes a compressor 2, an indoor condenser 3, a first control valve unit 203, an outdoor heat exchanger 5, a second control valve unit 205, an evaporator 7 and an accumulator 8, which are connected by piping. It has a connected refrigeration cycle. The indoor condenser 3 and the outdoor heat exchanger 5 are configured to operate in parallel as a condenser, and the evaporator 7 and the outdoor heat exchanger 5 are configured to operate in parallel as an evaporator. A first refrigerant circulation passage through which refrigerant circulates during cooling operation (dehumidification) and heating operation (dehumidification), a second refrigerant circulation passage through which refrigerant circulates during heating operation and defrosting operation, and refrigerant circulates during cooling operation A third refrigerant circulation passage is formed.

  The first refrigerant circulation passage is a passage through which the refrigerant circulates like the compressor 2 → the indoor condenser 3 → the second control valve unit 205 → the evaporator 7 → the second control valve unit 205 → the accumulator 8 → the compressor 2. . The second refrigerant circulation passage is a passage through which the refrigerant circulates like compressor 2 → indoor condenser 3 → second control valve unit 205 → outdoor heat exchanger 5 → first control valve unit 203 → accumulator 8 → compressor 2. It is. The third refrigerant circulation passage is as follows: compressor 2 → first control valve unit 203 → outdoor heat exchanger 5 → second control valve unit 205 → evaporator 7 → second control valve unit 205 → accumulator 8 → compressor 2 This is a passage through which the refrigerant circulates.

  The refrigerant flow through the outdoor heat exchanger 5 is reversed between when the second refrigerant circulation passage is opened and when the third refrigerant circulation passage is opened. That is, the refrigerant inlet and outlet in the outdoor heat exchanger 5 are switched between when the second refrigerant circulation passage is opened and when the third refrigerant circulation passage is opened. The second passage 22 connected to the outlet of the indoor condenser 3 branches downstream, the first branch passage 27 on one side thereof is connected to the evaporator 7, and the second branch passage 28 on the other side is connected to the outdoor heat exchanger 5. Connected to.

  The first refrigerant circulation passage is configured by connecting the first passage 21, the second passage 22, the first branch passage 27, and the fourth passage 24. The second refrigerant circulation passage is configured by connecting the first passage 21, the second passage 22, the second branch passage 28, the third passage 23, and the bypass passage 225. The third refrigerant circulation passage is configured by connecting the first passage 21, the third passage 23, and the fourth passage 24. And in order to implement | achieve such switching of a refrigerant circulation path, the 1st control valve unit 203 is provided in the connection part of the indoor condenser 3 and the outdoor heat exchanger 5, and the indoor condenser 3 and the outdoor heat exchanger are provided. A second control valve unit 205 is provided at the connection between the evaporator 5 and the evaporator 7.

  The first control valve unit 203 is configured by assembling a differential pressure valve 50, an on-off valve 52, and a superheat degree control valve 54 in a common body. The differential pressure valve 50 operates autonomously so that the differential pressure before and after (the differential pressure between the inlet side pressure of the indoor condenser 3 and the inlet side pressure of the outdoor heat exchanger 5) becomes a set differential pressure corresponding to the supply current value. It is a constant differential pressure valve (solenoid valve). In the present embodiment, a solenoid is used as an actuator for driving the valve portion of the differential pressure valve 50, but an electric motor such as a stepping motor may be used. The differential pressure valve 50 is driven during the dehumidifying operation to execute differential pressure control, and the condensation pressure in the indoor condenser 3 is maintained higher than the condensation pressure in the outdoor heat exchanger 5 by a set differential pressure, whereby in the indoor condenser 3 Prevents the refrigerant temperature from excessively decreasing. Specifically, a condensation pressure (temperature) that can warm the feet of the driver appropriately can be obtained.

  The on-off valve 52 is provided upstream of the superheat control valve 54 in the bypass passage 225. The on-off valve 52 is a two-way electromagnetic valve that includes a valve portion that opens and closes the bypass passage 225 and a solenoid that drives the valve portion. The flow of the refrigerant to the accumulator 8 through the bypass passage 225 is permitted by opening the on-off valve 52. In the present embodiment, as the on-off valve 52, an on-off valve (on / off valve) that opens and closes the valve portion depending on whether the solenoid is energized is used. The actuator that drives the valve portion of the on-off valve 52 may not be a solenoid, but may be an electric motor such as a stepping motor.

  The superheat degree control valve 54 functions as an “evaporation pressure adjusting valve” that adjusts the evaporation pressure when the outdoor heat exchanger 5 functions as an outdoor evaporator. The superheat degree control valve 54 controls the flow of the refrigerant so that the superheat degree approaches a predetermined superheat degree (set superheat degree SH) when the superheat degree (superheat) is generated on the outlet side. To do. In the present embodiment, as the superheat degree control valve 54, a mechanical control valve having a temperature sensing part that senses the temperature and pressure of the refrigerant on the outlet side (downstream side of the superheat degree control valve 54) and drives the valve part. Is used. The superheat degree control valve 54 reduces the opening degree of the valve if the detected superheat degree is larger than the set superheat degree SH and raises the evaporation pressure of the outdoor heat exchanger 5, whereby the refrigerant passing through the outdoor heat exchanger 5 The amount of heat exchange with the external air is reduced, thereby reducing the degree of superheat to approach the set superheat degree SH. On the contrary, if the detected superheat degree is smaller than the set superheat degree SH, the superheat degree control valve 54 increases the valve opening degree and decreases the evaporation pressure of the outdoor heat exchanger 5, thereby causing the outdoor heat exchanger 5 to open. The amount of heat exchange between the refrigerant passing through 5 and the external air is increased, thereby increasing the degree of superheat and bringing it closer to the set degree of superheat SH. Thus, the superheat degree control valve 54 operates autonomously so that the superheat degree on the outlet side approaches the set superheat degree SH.

  On the other hand, the second control valve unit 205 includes a flow control valve 60, a supercooling degree control valve 62 (first supercooling degree control valve), and a supercooling degree control valve 64 (second supercooling degree control) in a common body. Valve), a differential pressure valve 66, and a superheat control valve 68 are assembled. The flow control valve 60 is provided in the second branch passage 28, and the supercooling degree control valve 62 is provided in the first branch passage 27. A supercooling degree control valve 64 and a differential pressure valve 66 are arranged from the upstream side between the connection point of the third passage 23 with the second branch passage 28 and the connection point of the first branch passage 27. .

  The flow rate control valve 60 is configured as a proportional valve whose opening degree is autonomously adjusted to a set opening degree corresponding to the supply current value to the actuator. In the present embodiment, a stepping motor is employed as an actuator that drives the valve portion of the flow control valve 60, but a solenoid may be used. The flow control valve 60 is basically controlled to any one of a fully open state, a large diameter control state, a small diameter control state, and a valve closed state. The large-diameter control state is a state in which the opening degree is large although the full-open state is not reached, and the small-diameter control state is a state in which the opening degree is small although the valve opening state is not reached.

  The flow control valve 60 also functions as an expansion device by small diameter control. During heating operation, the opening / closing valve 52 is opened and the bypass passage 25 is opened as described later, while the opening degree of the flow control valve 60 (that is, the opening degree of the second passage 22) is adjusted. . For this reason, according to the opening degree of the flow control valve 60, the flow volume of the refrigerant | coolant supplied to the outdoor heat exchanger 5 is adjusted. That is, the flow rate control valve 60 is configured such that the refrigerant flow rate from the indoor condenser 3 toward the outdoor heat exchanger 5 and the refrigerant flow rate that bypasses the outdoor heat exchanger 5 and is supplied to the evaporator 7 (the refrigerant flow rate that flows through the bypass passage 25). ) Function as a flow rate adjustment valve to adjust the ratio.

  The supercooling degree control valve 62 also functions as an “expansion device” that squeezes and expands the refrigerant introduced from the indoor condenser 3 via the second passage 22 and leads it to the downstream side. The supercooling degree control valve 62 operates in the valve opening direction when the supercooling degree on the outlet side of the indoor condenser 3 becomes larger than the set value SC, and increases the flow rate of the refrigerant flowing through the indoor condenser 3. When the flow rate of the refrigerant increases in this way, the condensing capacity per unit flow rate of the refrigerant in the indoor condenser 3 decreases, so that the degree of supercooling decreases. Conversely, when the degree of supercooling on the outlet side of the indoor condenser 3 becomes smaller than the set value SC, the supercooling degree control valve 62 operates in the valve closing direction to decrease the flow rate of the refrigerant flowing through the indoor condenser 3. . When the flow rate of the refrigerant is thus reduced, the condensation capacity per unit flow rate of the refrigerant in the indoor condenser 3 is increased, so that the degree of supercooling is increased. Thus, the supercooling degree control valve 62 operates autonomously so that the supercooling degree at the inlet (the outlet side of the indoor condenser 3) becomes the set value SC.

  The supercooling degree control valve 64 functions as an “expansion device” that expands and expands the refrigerant derived from the outdoor heat exchanger 5 or the refrigerant supplied via the bypass passage 25 to the evaporator 7 side. The supercooling degree control valve 64 operates in the valve opening direction when the supercooling degree on the outlet side of the outdoor heat exchanger 5 becomes larger than the set value SC during the cooling operation, and controls the flow rate of the refrigerant flowing through the outdoor heat exchanger 5. increase. When the flow rate of the refrigerant increases in this way, the condensing capacity per unit flow rate of the refrigerant in the outdoor heat exchanger 5 decreases, so that the degree of supercooling decreases. Conversely, when the degree of supercooling on the outlet side of the outdoor heat exchanger 5 becomes smaller than the set value SC, the supercooling degree control valve 64 operates in the valve closing direction, and the flow rate of the refrigerant flowing through the outdoor heat exchanger 5 is reduced. Let When the flow rate of the refrigerant decreases in this way, the condensation capacity per unit flow rate of the refrigerant in the outdoor heat exchanger 5 increases, so that the degree of supercooling increases. The supercooling degree control valve 64 operates autonomously so that the supercooling degree at the inlet (the outlet side of the outdoor heat exchanger 5) becomes the set value SC. In this embodiment, the setting values of the supercooling degree of the supercooling degree control valve 64 and the supercooling degree control valve 62 are made equal, but different setting values may be set.

  The differential pressure valve 66 is provided on the downstream side of the supercooling degree control valve 64. The differential pressure valve 66 is configured as a mechanical valve that prevents the refrigerant from flowing back to the supercooling degree control valve 64 side in the third passage 23, and when the front-rear differential pressure becomes equal to or higher than the set valve opening differential pressure. To open.

  The superheat degree control valve 68 controls the flow of the refrigerant so that the superheat degree approaches a predetermined superheat degree (set superheat degree SH) when the superheat degree (superheat) is generated on the outlet side. To do. In the present embodiment, as the superheat degree control valve 68, a mechanical control valve having a temperature sensing part that senses the temperature and pressure of the refrigerant on the outlet side (downstream side of the superheat degree control valve 68) and drives the valve part. Is used. The superheat degree control valve 68 reduces the opening degree of the valve if the detected superheat degree is larger than the set superheat degree SH, and raises the evaporation pressure of the evaporator 7, so that the refrigerant passing through the evaporator 7 and the external air The amount of heat exchange is reduced, thereby reducing the degree of superheat to approach the set degree of superheat SH. Conversely, if the detected superheat degree is smaller than the set superheat degree SH, the superheat degree control valve 68 passes through the evaporator 7 by increasing the valve opening and lowering the evaporation pressure of the evaporator 7. The amount of heat exchange between the refrigerant and the outside air is increased, thereby increasing the degree of superheat and bringing it closer to the set degree of superheat SH. As described above, the superheat degree control valve 68 operates autonomously so that the superheat degree on the outlet side thereof approaches the set superheat degree SH. In the present embodiment, the set superheat degree of the superheat degree control valve 68 and the set superheat degree of the superheat degree control valve 54 are set equal, but they may be set differently.

  The control unit 100 determines a set opening degree of the flow control valve 60 based on predetermined external information detected by various sensors such as the temperature inside and outside the vehicle interior, the temperature of the air blown from the evaporator 7 and the like. A control pulse signal is output to the stepping motor so that the set opening degree is obtained. By such control, as shown in the figure, the compressor 2 introduces the refrigerant having the suction pressure Ps through the suction chamber, compresses the refrigerant, and discharges it as the refrigerant having the discharge pressure Pd. As shown in the figure, the upstream side of the flow control valve 60 and the supercooling degree control valve 62 becomes a high pressure upstream pressure P1, and the downstream side of the supercooling degree control valve 62 is a low pressure downstream side pressure as controlled by the control unit 100. P3. Further, the downstream side of the flow rate control valve 60 and the upstream side of the supercooling degree control valve 64 become the intermediate pressure P2.

  Next, operation | movement of the refrigerating cycle of this embodiment is demonstrated. FIG. 5 is an explanatory diagram showing the operation of the vehicle air conditioner. (A) shows the state during cooling operation, (B) shows the state during dehumidification operation, (C) shows the state during specific heating operation, and (D) shows the state during defrosting operation. Yes. The upper part of each figure shows a Mollier diagram for explaining the operation of the refrigeration cycle. The horizontal axis represents enthalpy, and the vertical axis represents various pressures.

  As shown in FIG. 5A, during the cooling operation, the differential pressure valve 50 is opened and the on-off valve 52 is closed in the first control valve unit 203. The differential pressure valve 50 is fully opened without performing differential pressure control. On the other hand, in the second control valve unit 205, the flow control valve 60 is closed. Since the bypass passage 225 is blocked by the closing of the on-off valve 52, the refrigerant discharged from the compressor 2 is guided to the outdoor heat exchanger 5. At this time, the outdoor heat exchanger 5 functions as an outdoor condenser. That is, the refrigerant discharged from the compressor 2 circulates in the first refrigerant circulation passage so as to pass through the indoor condenser 3, the supercooling degree control valve 62, the evaporator 7, the superheat degree control valve 68, and the accumulator 8. Then, the third refrigerant circulation passage is passed through the differential pressure valve 50, the outdoor heat exchanger 5, the supercooling degree control valve 64, the evaporator 7, the superheat degree control valve 68, and the accumulator 8 on the other side. Circulate and return to the compressor 2.

  That is, the high-temperature and high-pressure gas refrigerant discharged from the compressor 2 is condensed by passing through the indoor condenser 3 on the one hand and the outdoor heat exchanger 5 on the other hand. Then, the refrigerant passing through the indoor condenser 3 is adiabatically expanded by the supercooling degree control valve 62 and is introduced into the evaporator 7 as a cold / low pressure gas-liquid two-phase refrigerant. At this time, the supercooling degree control valve 62 autonomously adjusts the opening degree of the valve portion so that the supercooling degree on the outlet side (point c) of the indoor condenser 3 becomes the set value SC.

  Further, the refrigerant passing through the outdoor heat exchanger 5 is adiabatically expanded by the supercooling degree control valve 64 and is introduced into the evaporator 7 as a cold / low pressure gas-liquid two-phase refrigerant. At this time, the supercooling degree control valve 64 autonomously adjusts the opening degree of the valve portion so that the supercooling degree on the outlet side (point e) of the outdoor heat exchanger 5 becomes the set value SC. The refrigerant introduced into the inlet of the evaporator 7 evaporates in the process of passing through the evaporator 7 and cools the air in the passenger compartment.

  As shown in FIG. 5B, during the dehumidifying operation, the differential pressure valve 50 performs differential pressure control in the first control valve unit 203. For this reason, control is performed so that the differential pressure across the differential pressure valve 50 becomes the set differential pressure ΔP. As a result, the condensation pressure (condensation temperature) of the indoor condenser 3 is maintained higher than the condensation pressure (condensation temperature) of the outdoor heat exchanger 5, and the temperature inside the vehicle compartment is suppressed from being lowered more than necessary. Also in this case, the supercooling degree control valve 62 autonomously adjusts the opening degree of the valve portion so that the supercooling degree on the outlet side (point c) of the indoor condenser 3 becomes the set value SC. The supercooling degree control valve 64 autonomously adjusts the opening degree of the valve portion so that the supercooling degree on the outlet side (point e) of the outdoor heat exchanger 5 becomes the set value SC. In the present embodiment, the supercooling degree on the outlet side of the indoor condenser 3 and the supercooling degree on the outlet side of the outdoor heat exchanger 5 are set to the same set value. However, in the modification, these set values are set. May be different from each other.

  As shown in FIG. 5C, during the specific heating operation, the differential pressure valve 50 is closed in the first control valve unit 203 and the on-off valve 52 is opened, while the flow rate in the second control valve unit 205. The opening degree of the control valve 60 is controlled. That is, the small-diameter control of the flow control valve 60 is performed and the opening degree thereof is adjusted, so that the ratio of the flow rate of the refrigerant toward the evaporator 7 and the outdoor heat exchanger 5 is adjusted. At this time, the outdoor heat exchanger 5 functions as an outdoor evaporator. That is, the refrigerant discharged from the compressor 2 circulates in the first refrigerant circulation passage so as to pass through the indoor condenser 3, the supercooling degree control valve 62, the evaporator 7, the superheat degree control valve 68, and the accumulator 8. Return to the compressor 2, and on the other hand, circulate through the second refrigerant circulation passage through the indoor condenser 3, the flow control valve 60, the outdoor heat exchanger 5, the on-off valve 52, the superheat degree control valve 54, and the accumulator 8. And it returns to the compressor 2.

  That is, the high-temperature and high-pressure gas refrigerant discharged from the compressor 2 is condensed through the indoor condenser 3. One of the refrigerants derived from the indoor condenser 3 is adiabatically expanded by the flow control valve 60 to become a cold / low pressure gas-liquid two-phase refrigerant, which is supplied to the outdoor heat exchanger 5 and evaporates. The other refrigerant derived from the indoor condenser 3 is adiabatically expanded by the supercooling degree control valve 62 to become a cold / low pressure gas-liquid two-phase refrigerant, which is supplied to the evaporator 7 and evaporates. At this time, the ratio of evaporation in both the outdoor heat exchanger 5 and the evaporator 7 is controlled by the opening degree of the flow control valve 60. Thereby, the evaporation amount in the evaporator 7 can be secured, and the dehumidifying function can be secured. On the other hand, the flow rate of the refrigerant supplied to the evaporator 7 is adjusted by the supercooling degree control valve 62 so that the supercooling degree on the outlet side of the indoor condenser 3 becomes the set value SC.

  In this specific heating operation, the dehumidifying operation is performed satisfactorily. The outline of the dehumidifying control is as follows. That is, as shown in FIG. 5C, the predetermined supercooling degree SC at the outlet of the indoor condenser 3 is maintained by the supercooling degree control valve 62 (point c), so that the condensing capacity in the indoor condenser 3 is maintained. Is maintained properly, and efficient heat exchange is performed in each of the outdoor heat exchanger 5 (outdoor evaporator) and the evaporator 7 (indoor evaporator). At this time, since the state of the refrigerant at the inlet of the compressor 2 is always maintained on the saturated vapor pressure curve by the accumulator 8 (point a), the state of the refrigerant at the outlet of the evaporator 7 (point g) is controlled by superheat. It changes so that it may balance with the state (h point) of the refrigerant | coolant of the exit of the valve 54. FIG.

  That is, as shown in the figure, when superheat is generated on the outlet side of the superheat degree control valve 54, the wettability (g point) of the refrigerant at the outlet of the evaporator 7 is the refrigerant at the outlet of the superheat degree control valve 54. Balance with the degree of superheat (h point). Conversely, when the degree of superheat occurs on the outlet side of the superheat degree control valve 68, the wetness (point (e)) at the outlet of the outdoor heat exchanger 5 is the outlet side of the superheat degree control valve 68. The degree of superheat (point (i)) is balanced.

  Further, during the defrosting operation, as shown in FIG. 5D, the differential pressure valve 50 is closed while the on-off valve 52 is opened, and the flow control valve 60 is opened. At this time, the flow control valve 60 performs large diameter control. As a result, the high-temperature and high-pressure gas refrigerant (hot gas) discharged from the compressor 2 passes through the flow control valve 60 and is supplied to the outdoor heat exchanger 5. At this time, since the refrigerant on the outlet side of the outdoor heat exchanger 5 is not supercooled (point e), the supercooling degree control valve 64 maintains the closed state. For this reason, supply of the refrigerant | coolant to the evaporator 7 is interrupted | blocked. In a state where the defrosting operation is stable, as shown by a solid line in the figure, the refrigerant derived from the outdoor heat exchanger 5 is controlled on the saturated vapor line by being introduced into the accumulator 8 (point e). On the other hand, when the superheat degree is generated on the outlet side of the superheat degree control valve 54 due to insufficient liquid refrigerant in the accumulator 8, the superheat degree control valve 54 sets the superheat degree as shown by the dotted line in the figure. The flow of the refrigerant is controlled so as to approach the superheat degree SH.

Next, a specific configuration of the second control valve unit 205 will be described. FIG. 6 is a cross-sectional view illustrating a specific configuration of the second control valve unit.
The second control valve unit 205 is configured as a collective valve in which a flow control valve 60, a supercooling degree control valve 62, a supercooling degree control valve 64, a differential pressure valve 66, and a superheat degree control valve 68 are assembled in a common body 250. Yes. As shown in the figure, the flow control valve 60 whose drive unit is exposed from the body 250 is an electric drive valve, whereas the supercooling degree control valve 62, the supercooling degree control valve 64, and the difference that are entirely accommodated in the body 250. The pressure valve 66 and the superheat degree control valve 68 are mechanical valves.

  The body 250 has a bottomed cylindrical main body obtained by cutting a metal material, and has an insertion port 251 at the end opposite to the bottom of the main body. An inlet port 252, an inlet / outlet port 254, an outlet port 256, an outlet port 258, and an inlet port 260 are provided on the side portion of the body 250 from above. Inside the body 250, there are the superheat degree control valve 68, the supercooling degree control valve 62, the supercooling degree control valve 64 and the differential pressure valve 66 as a whole, and the half of the flow control valve 60 (valve body 301). Is incorporated. The body 250 incorporates a plurality of passage forming members for partitioning the refrigerant passage. The insertion port 251 of the body 250 is sealed by a motor unit 302 that is a drive unit of the flow control valve 60.

  That is, the body 250 has a shape in which the inner diameter gradually increases from the bottom toward the insertion port 251, and the superheat degree control valve 68, the passage forming member 264, the supercooling degree control valve 62, from the bottom side. The passage forming member 266, the differential pressure valve 66, the supercooling degree control valve 64, the passage forming member 268, and the flow rate control valve 60 are arranged in order. The passage forming members 264, 266, 268 are all obtained by molding a resin material.

  The superheat degree control valve 68 is configured such that a valve driving body 272 and a bellows 274 are coaxially accommodated in a body 270 obtained by press molding. An inlet port for introducing the refrigerant is provided at a portion of the body 270 facing the introduction port 260, and an outlet port for discharging the refrigerant is provided at a portion opposite to the outlet port 258. A valve hole 276 is provided between the inlet port and the outlet port. A valve body provided integrally with the valve drive body 272 contacts and separates from the valve hole 276 from the downstream side to adjust the valve opening. The bellows 274 is filled with a reference gas of the same type as the refrigerant gas that circulates in the refrigeration cycle, and senses the temperature and pressure of the refrigerant flowing through the internal passage on the outlet port side (downstream side of the valve portion). The valve driver 272 is driven so that the superheat degree of the refrigerant on the outlet side (downstream side of the valve portion) of the superheat degree control valve 68 becomes the set superheat degree SH. The valve driver 272 is provided with a cancel structure that cancels the influence of the upstream pressure Pin acting on the valve body.

  According to the superheat degree control valve 68, when the superheat degree is generated on the downstream side of the valve portion (the outlet side of the superheat degree control valve), the superheat degree is controlled to become the set superheat degree SH. That is, when the superheat degree on the downstream side becomes larger than the set superheat degree SH in the superheat degree control state, the bellows 274 senses a high temperature and operates in the valve closing direction. As a result, the downstream pressure Pout is decreased and the upstream pressure Pin is increased because the valve opening is decreased, so that the heat exchange amount in the evaporator 7 on the upstream side is reduced, resulting in the overheating on the downstream side. The degree also decreases. Conversely, when the superheat degree becomes smaller than the set superheat degree SH, the bellows 274 senses the low temperature and operates in the valve opening direction. As a result, since the valve opening increases, the downstream pressure Pout increases and the upstream pressure Pin decreases, so that the amount of heat exchange in the upstream evaporator 7 increases, resulting in downstream overheating. The degree changes in the direction of increasing. In this way, the degree of superheat on the downstream side of the valve part is maintained at the set superheat degree SH. Note that controlling the degree of superheat on the downstream side of the valve portion in this way adjusts the state of the refrigerant on the upstream side of the valve portion (the evaporation state in the evaporator 7 on the upstream side).

  A passage forming member 264 is disposed immediately above the superheat degree control valve 68. The passage forming member 264 has a bottomed cylindrical shape, and an O-ring for sealing is fitted on the outer peripheral surface thereof. By the passage forming member 264, a refrigerant passage in which the superheat degree control valve 68 is disposed and a refrigerant passage in which the supercooling degree control valve 62 is disposed are partitioned in the body 250. A supercooling degree control valve 62 is disposed immediately above the passage forming member 264. The passage forming member 266 has a cylindrical shape and supports the supercooling degree control valve 62 between the passage forming member 264 and the passage forming member 264. A communication hole that communicates the inside and the outside is provided on the surface of the passage forming member 266 that faces the outlet port 256. The valve portion of the supercooling degree control valve 62 is inserted into the lower end opening of the passage forming member 266.

  The supercooling degree control valve 62 includes a valve portion that squeezes and expands the refrigerant introduced from the upstream side, and a power element 280 that opens and closes the valve portion. A communication groove parallel to the axis is provided at a predetermined position on the outer peripheral surfaces of the passage forming members 266 and 268, and a part of the refrigerant introduced from the introduction port 252 controls the degree of supercooling through the communication groove. Directed to the inlet port of valve 62. The supercooling degree control valve 62 is configured by accommodating a valve body 284 in a press-molded body 282. A power element 280 is integrally provided at the lower end of the body 282. The upper half of the body 282 has a reduced diameter, and a valve hole 286 is formed in the reduced diameter portion. The lower half of the body 282 is provided with an inlet port for communication between the inside and the outside, and the upper half is provided with an outlet port for communication between the inside and the outside. A back pressure chamber 288 is formed by sealing the upper end of the body 282 with a spring receiver. A spring for biasing the valve body 284 in the valve opening direction is interposed between the spring receiver and the valve body 284. The valve body 284 opens and closes the valve portion by contacting and separating from the upstream side of the valve hole 286.

  The power element 280 includes a hollow housing and a diaphragm arranged so as to partition the inside of the housing into a sealed space and an open space. The sealed space is filled with a mixed gas of refrigerant gas and nitrogen gas that circulates in the refrigeration cycle as a reference gas. A communication path is formed so as to penetrate the valve body 284 in the axial direction, and the refrigerant introduced from the inlet port is also guided to the back pressure chamber 288 via the communication path. In this embodiment, since the effective diameter of the valve body 284 in the back pressure chamber 288 and the effective diameter of the valve hole 286 are equal, the upstream pressure P1 acting on the valve body 284 is cancelled.

  According to the supercooling degree control valve 62, when the supercooling degree becomes larger than the set value SC in the supercooling degree control state, the power element 280 senses a low temperature and operates in the valve opening direction. As a result, the valve opening increases, so the upstream pressure P1 decreases, and the degree of supercooling decreases. On the contrary, when the degree of supercooling becomes smaller than the set value SC, the power element 280 senses a high temperature and operates in the valve closing direction. As a result, since the valve opening becomes small, the upstream pressure P1 increases, and the degree of supercooling increases. In this way, the degree of supercooling is maintained at the set value SC.

  The valve portion of the supercooling degree control valve 64 is inserted through the upper end opening of the passage forming member 266. The passage forming member 268 has a stepped cylindrical shape, and supports the supercooling degree control valve 64 between the passage forming member 266 and the passage forming member 266. A communication hole that communicates the inside and the outside is provided on the surface of the passage forming member 268 facing the introduction / exit port 254 and the surface facing the introduction port 252. And the valve hole 290 is provided in the boundary part of these communicating holes.

  The supercooling degree control valve 64 has a structure similar to that of the supercooling degree control valve 62, and includes a valve portion that throttles and expands the refrigerant introduced from the upstream side, and a power element 280 that opens and closes the valve portion. Yes. However, a communication hole is provided in the spring receiver of the supercooling degree control valve 64, and a differential pressure valve 66 is provided so as to surround the communication hole.

  That is, the differential pressure valve 66 has a bottomed stepped cylindrical valve body 292 and is disposed so as to surround the lower half of the supercooling degree control valve 64 from the outside. A valve member made of a ring-shaped elastic body is fitted to the upper end opening of the valve body 292, and the valve member is attached to and detached from the body 289 of the supercooling degree control valve 64, whereby the supercooling degree control valve 64 is attached. It is comprised so that the exit port of can be opened and closed. A spring for biasing the differential pressure valve 66 in the valve closing direction is interposed between the differential pressure valve 66 and the passage forming member 266. The passage forming member 268 is formed with a communication passage that communicates the pressure chamber in which the power element 280 of the supercooling degree control valve 64 is disposed with the inlet / outlet port 254. For this reason, a part of the refrigerant introduced from the inlet / outlet port 254 is guided to the inlet port of the supercooling degree control valve 64.

  According to the supercooling degree control valve 64, when the supercooling degree becomes larger than the set value SC in the supercooling degree control state, the power element 280 senses a low temperature and operates in the valve opening direction. As a result, the valve opening increases, so the upstream pressure P2 decreases, and the degree of supercooling decreases. On the contrary, when the degree of supercooling becomes smaller than the set value SC, the power element 280 senses a high temperature and operates in the valve closing direction. As a result, since the valve opening becomes small, the upstream pressure P2 increases, and the degree of supercooling increases. In this way, the degree of supercooling is maintained at the set value SC.

  The flow control valve 60 is configured as an electric valve driven by a stepping motor, and is configured by assembling a valve main body 301 and a motor unit 302. The valve body 301 includes a first valve 305 having a small diameter and a second valve 306 having a large diameter in a coaxial manner. Inside the passage forming member 268, a large-diameter valve body 308, a small-diameter valve body 310, and a valve operating body 312 are arranged coaxially. The valve body 308 contacts and separates from the valve hole 290 from the upstream side to open and close the second valve 306. A valve hole 314 is formed so as to penetrate the center of the valve body 308 in the axial direction. The valve body 310 contacts and separates from the valve hole 314 from the upstream side to open and close the first valve 305. A high pressure chamber communicating with the introduction port 252 is formed on the upstream side of the valve hole 290 and the valve hole 314, and a low pressure chamber communicating with the introduction / exit port 254 is formed on the downstream side of the valve hole 290 and the valve hole 314.

  The motor unit 302 is configured as a stepping motor including a rotor 320 and a stator 322. The valve operating body 312 supports the valve body 310 and is fitted to the rotor 320 of the motor unit 302. A spring that biases the valve body 310 in the valve closing direction is interposed between the valve operating body 312 and the valve body 310. The valve operating body 312 rotates by receiving the rotational driving force of the motor unit 302 and converts the rotational force into a translational force. That is, the valve operating body 312 is displaced in the axial direction by rotation, and drives the valve body 310 in the opening / closing direction.

  The control unit 100 calculates the number of drive steps of the stepping motor according to the set opening, and supplies a drive current (drive pulse) to the excitation coil of the stator 322. Thereby, the rotor 320 is rotated, while the valve operating body 312 is rotationally driven, and the opening degree of the first valve 305 having a small diameter and the second valve 306 having a large diameter is adjusted to a set opening degree.

  The preferred embodiments of the present invention have been described above. However, the present invention is not limited to the specific embodiments, and various modifications can be made within the scope of the technical idea of the present invention. Nor.

  In the above-described embodiment, an example in which the vehicle air conditioning apparatus including the collective valve of the present invention is applied to an electric vehicle has been described. However, the present invention is provided to an automobile equipped with an internal combustion engine and a hybrid automobile equipped with an internal combustion engine and an electric motor It goes without saying that it is possible. In the above-described embodiment, an example in which an electric compressor is employed as the compressor 2 has been described. However, a variable capacity compressor that performs variable capacity using the rotation of the engine may be employed.

  DESCRIPTION OF SYMBOLS 1 Vehicle air conditioner, 2 Compressor, 3 Indoor condenser, 5 Outdoor heat exchanger, 6 Liquid tank, 7 Evaporator, 8 Accumulator, 9 Expansion valve, 21 1st passage, 22 2nd passage, 23 3rd passage 24, 4th passage, 25, 26 Bypass passage, 27 1st branch passage, 28 2nd branch passage, 32 Differential pressure valve, 41, 42 Switching valve, 43 On-off valve, 44 Orifice, 45 Check valve, 50 Differential pressure valve, 52 On-off valve, 54 Superheat control valve, 60 Flow control valve, 62, 64 Supercooling control valve, 66 Differential pressure valve, 68 Superheat control valve, 100 Control unit, 102 Valve body, 104 Solenoid, 105 Body, 106 Main Valve, 108 Sub valve, 110 Pilot valve, 112 First body, 114 Second body, 116 Fitting hole 120 inlet port, 122,124 outlet port, 126 first passage forming member, 128 second passage forming member, 132 main valve hole, 140 main valve body, 156 pilot valve hole, 160 pilot valve body, 172 valve seat forming portion, 174 Sub valve hole, 178 Sub valve body, 188 Sealing member, 201 Vehicle air conditioner, 203 First control valve unit, 205 Second control valve unit, 225 Bypass passage, 250 body, 251 insertion port, 252 introduction port, 254 Inlet / out port, 256, 258 Outlet port, 260 Inlet port, 264, 266, 268 Passage forming member, 272 Valve driver, 276 Valve hole, 280 Power element, 284 Valve body, 286, 290 Valve hole, 292 Valve body 301 Valve body 302 Motor unit, 305 first valve, 306 second valve, 308, 310 valve body, 312 valve operating body, 314 valve hole, 320 rotor, 322 stator.

Claims (4)

A collective valve including a plurality of control valves for controlling the flow of the working fluid,
An internal space for accommodating the valve portions of the plurality of control valves is formed, an insertion port for inserting the valve portion, an introduction port for introducing the working fluid, and a derivation for deriving the working fluid A shared body with a port,
A passage forming member that is inserted into the body from the insertion port and that defines an internal passage that connects the introduction port and the outlet port;
With
An assembly valve, wherein an insertion port of the body is sealed by a part of any of the plurality of control valves. The body is formed by processing a metal material,
The collecting valve according to claim 1, wherein the passage forming member is formed by processing a resin material. As the control valve, including an electric drive valve having a drive unit that opens and closes the valve unit by energization,
The collecting valve according to claim 1 or 2, wherein the insertion port of the body is sealed by a drive portion of the electric drive valve. As the control valve, including a mechanical valve that mechanically opens and closes the valve portion,
The collective valve according to claim 3, wherein the entire mechanical valve is accommodated in an internal space of the body.

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