JPWO2021064812A1 - Integrated valve - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide an integrated valve capable of easily forming an orifice. An integrated valve is formed in a support base, a gas-liquid separation chamber that takes in a refrigerant, separates the gas and liquid, and discharges a gaseous refrigerant and a liquid refrigerant separately, and a gas and liquid. It has a first flow path for refrigerant intake that extends from the separation chamber and has an indoor condenser port connected to the indoor condenser at the end, and an outdoor evaporator port that extends from the gas-liquid separation chamber and connects to the outdoor evaporator at the end. A second flow path for a liquid refrigerant, a third flow path for a gaseous refrigerant having a compressor port extending from the gas-liquid separation chamber and connected to a compressor input port at the end, and a third flow path. A differential pressure valve that is provided in the middle of the process and normally closes the third flow path and opens the third flow path according to the pressure of the second flow path, and the second flow. It is provided in the middle of the road and is made of a drive valve that is normally opened in the indoor heating mode and closed in the special indoor heating mode, and a material with lower thermal conductivity than the support base. , A heat insulating member that is assembled inside the support base and penetrates a part of the second flow path, and an upstream side of the valve port that is formed in the heat insulating member and is opened and closed by the drive valve in the second flow path. It is provided with an orifice that communicates with the downstream side. [Selection diagram] Fig. 4

Description

The present disclosure is incorporated in a heat pump cycle having an indoor condenser, an outdoor evaporator and a compressor, and the refrigerant from the indoor condenser is separated into gas and liquid, and whether or not the gaseous refrigerant is discharged to the compressor is switched to switch the heat cycle. Regarding the integrated valve that switches the heating mode.

As a conventional integrated valve, it has a metal body, a valve port that opens and closes in the middle of the flow path that penetrates the body is provided, and an orifice that communicates the upstream side and the downstream side of the valve port is provided in the body. The formed one is known (see, for example, Patent Document 1).

Japanese Patent No. 5772764 (paragraph [0010], FIG. 4)

In the conventional integrated valve described above, since the orifice is formed by drilling the orifice in the depth of the flow path of the body, there is a problem that it is difficult to form the orifice.

The invention of claim 1 made to solve the above problems is incorporated into a heat pump cycle having an indoor condenser, an outdoor evaporator and a compressor, and integrates the heat pump cycle to switch between a normal indoor heating mode and a special indoor heating mode. A valve, a support base, a gas-liquid separation chamber formed on the support base, taking in a refrigerant, separating the gas and liquid, and discharging the gaseous refrigerant and the liquid refrigerant separately, and the gas-liquid separation. For the first flow path for taking in the refrigerant having an indoor condenser port extending from the chamber and connected to the indoor condenser at the end, and for an outdoor evaporator extending from the gas-liquid separation chamber and connected to the outdoor evaporator at the end. A third stream for the gaseous refrigerant having a second flow path for the liquid refrigerant having a port and a compressor port extending from the gas-liquid separation chamber and connected to the input port of the compressor at the end. It is provided in the middle of the path and the third flow path, and is usually in a valve closed state in which the third flow path is blocked, and the third flow path is opened according to the pressure of the second flow path. A differential pressure valve that is in a valve state and a drive valve that is provided in the middle of the second flow path and is driven so as to be in a valve open state in the normal room heating mode and in a valve closed state in the special room heating mode. A heat insulating member formed of a material having a lower thermal conductivity than the support base, assembled inside the support base, and partially penetrating the second flow path, and a heat insulating member formed on the heat insulating member. It is an integrated valve including an orifice that connects between the upstream side and the downstream side of the valve opening that is opened and closed by the drive valve among the two flow paths.

Conceptual diagram of a heat pump cycle in which the integrated valve according to the first embodiment of the present disclosure is incorporated. Front perspective view of the integrated valve Rear perspective view of the integrated valve Regular cross-sectional view of the integrated valve when the solenoid valve is open Positive cross-sectional view of the integrated valve when the solenoid valve is closed Perspective view of heat insulating member BB sectional view of the lower base and the heat insulating member Side view of the heat insulating member assembled to the lower base

[First Embodiment]
Hereinafter, the valve 10 of the present embodiment will be described with reference to FIGS. 1 to 8. As shown in FIG. 1, the integrated valve 10 of the present embodiment is incorporated into, for example, the heat pump cycle 80 of an air conditioner of an electric vehicle or a hybrid vehicle traveling by a driving force of a motor. The heat pump cycle 80 can be switched to a heating mode for heating the interior of the vehicle, a cooling mode for cooling the interior of the vehicle, and the like.

The integrated valve 10 has an inflow port 13 into which the refrigerant flows in, and two outflow ports 14 and 15 in which the refrigerant flows out. As will be described later, the integrated valve 10 has a gas-liquid separation chamber 12 inside, and separates the refrigerant from the inflow port 13 into gas-liquid. The integrated valve 10 is capable of flowing out the gaseous refrigerant and the liquid refrigerant obtained by gas-liquid separation from the gas-phase outflow port 14 and the liquid-phase outflow port 15, respectively. Further, the integrated valve 10 is provided with a drive valve 50 (electromagnetic valve in the example of the present embodiment) inside, and the gas phase outflow port 14 can be opened and closed by opening and closing the drive valve 50. ..

Before explaining the details of the integrated valve 10, the heat pump cycle 80 will be described first. The heat pump cycle 80 is provided with, for example, a compressor 81 and an outdoor heat exchanger 83 (outdoor evaporator) arranged in the bonnet, an indoor condenser 82 and an indoor evaporator 84 arranged in the vehicle interior.

The compressor 81 sucks in the refrigerant, compresses it, and discharges it. The compressor 81 is provided with a low-pressure input port 81A for sucking the low-pressure refrigerant and an intermediate pressure input port 81B for merging with the refrigerant in the process of compressing from low pressure to high pressure, and an output port 81C for discharging the compressed refrigerant to the indoor condenser 82. Is provided.

The outdoor heat exchanger 83 exchanges heat between the outside air and the refrigerant flowing inside the outdoor heat exchanger 83. The outdoor heat exchanger 83 functions as an evaporator (outdoor evaporator) that absorbs heat and evaporates the refrigerant when the heat pump cycle 90 is in the heating mode, while as a radiator that dissipates the refrigerant when the heat pump cycle 90 is in the cooling mode. Function.

The indoor condenser 82 is arranged in the air conditioning unit in the vehicle interior and functions as a radiator (heats the vehicle interior) to dissipate the high-temperature and high-pressure refrigerant discharged from the compressor 81. In the cooling mode, the chamber condenser 82 is covered, for example, with a cover. Further, the indoor evaporator 84 is used in the cooling mode and absorbs heat from the air in the vehicle interior (cools the vehicle interior).

The inflow port 13 of the integrated valve 10 is connected to the output port 82B of the indoor capacitor 82 via the expansion valve 87. The gas phase outflow port 14 of the integrated valve 10 is connected to an intermediate pressure input port 81B, which is one of the two input ports of the compressor 81. The liquid phase outflow port 15 of the integrated valve 10 is connected to the input port of the outdoor heat exchanger 83.

The input port of the indoor evaporator 84 is connected to the output port of the outdoor heat exchanger 83 via the expansion valve 85. Further, a low pressure input port 81A of the compressor 81 is connected to the output port of the indoor evaporator 84. An on-off valve 86 is connected in parallel with the indoor evaporator 84 between the output port of the outdoor heat exchanger 83 and the low-pressure input port 81A of the compressor 81. In the heating mode, the on-off valve 86 is in the open state and the expansion valve 85 is in the closed state, while in the cooling mode, the on-off valve 86 is in the closed state and the expansion valve 85 is in the open state. That is, the refrigerant flows through the indoor evaporator 84).

In the heat pump cycle 80, as a heating mode, a normal room heating mode (hereinafter, referred to as a normal heating mode) and a special room heating mode (hereinafter, referred to as a special heating mode) are provided. In the normal heating mode, the drive valve 50 of the integrated valve 10 is opened, whereby the gas phase outflow port 14 of the integrated valve 10 is closed (FIG. 1 (A)). Here, in the special heating mode, the drive valve 50 of the integrated valve is closed. As a result, the special inflow path 89 from the gas phase outflow port 14 of the integrated valve 10 to the intermediate pressure input port 81B of the compressor 81 is opened (FIG. 1 (B)). Then, the heat pump cycle 80 functions as a gas injection cycle, and can easily warm the vehicle interior even when the outside air temperature is low and the vehicle interior is difficult to warm in the normal heating mode.

More specifically, in the normal heating mode, when the outside air temperature is extremely low, the outdoor evaporator (outdoor heat exchanger 83) cannot sufficiently absorb heat from the outside air. Therefore, it is considered that the pressure of the refrigerant in the flow path from the outdoor heat exchanger 83 to the compressor 81 does not increase and the flow rate of the refrigerant also decreases. It is considered that if the flow rate of the refrigerant decreases, the discharge pressure and temperature of the refrigerant from the compressor 81 do not rise, the heat radiation from the indoor condenser 82 also decreases, and the heating capacity decreases. On the other hand, in the special heating mode, the gas injection cycle separates the refrigerant before flowing into the outdoor heat exchanger 83 into gas and liquid, and returns the separated gas refrigerant to the compressor 81. As a result, the refrigerant before the pressure drops in the outdoor heat exchanger 83 is applied to the compressor 81, so that it is considered that the decrease in the discharge pressure of the refrigerant from the compressor 81 can be suppressed. As a result, it is considered possible to improve the heating performance. Details of the heat pump cycle 80 are also disclosed in, for example, Japanese Patent No. 5772764 and Japanese Patent Application Laid-Open No. 2017-53591.

Next, the details of the integrated valve 10 will be described. As shown in FIGS. 2 and 3, the integrated valve 10 has a vertically elongated support base 11 made of, for example, a metal, and includes a plurality of flow paths inside the support base 11. The integrated valve 10 of the present embodiment is arranged so that the longitudinal direction of the support base 11 is in the vertical direction when the integrated valve 10 is used (that is, when the integrated valve 10 is installed in the vehicle). In the following, in the support base 11, when the integrated valve 10 is used, the surface facing upward is referred to as the upper surface, the surface facing downward is referred to as the lower surface, and the like. Further, in FIG. 4, the surface of the support base 11 facing the front side of the paper surface is referred to as the front surface, the surface facing the back side of the paper surface is referred to as the rear surface, and the surfaces of the support base 11 facing the left side and the right side are referred to as the left surface and the right surface, respectively. do.

As shown in FIG. 4, the gas-liquid separation chamber 12 described above is provided inside the support base 11. The gas-liquid separation chamber 12 is a columnar chamber extending in the vertical direction, and a cylindrical body 12A hangs from the ceiling coaxially with the central axis. The inflow port 13 communicates with the upper part of the inner peripheral surface of the gas-liquid separation chamber 12.

The gas-liquid separation chamber 12 is of a centrifugal separation type, and the refrigerant from the indoor condenser 82 flowing in from the inflow port 13 swirls along the inner peripheral surface of the gas-liquid separation chamber 12, and the centrifugal force generated by this swirl causes the refrigerant to swirl. The refrigerant is separated into a gaseous refrigerant and a liquid refrigerant. The separated gaseous refrigerant passes through the inside of the cylindrical body 12A and goes upward, and the separated liquid refrigerant falls below the gas-liquid separation chamber 12.

A first straight hole portion 21 and a second straight hole portion 31 extending in parallel with each other are formed on the lower side and the upper side of the gas-liquid separation chamber 12. The first straight hole portion 21 extends from the right surface of the support base 11 to a position closer to the left surface, and the left end portion of the first straight hole portion 21 is the above-mentioned liquid phase outflow port 15 extending from the front surface of the support base 11. Communicating. The right end of the first straight hole 21 is a first valve mounting portion that is closed by the support body 53 of the drive valve 50. The drive valve 50 includes a valve body 51 that moves linearly in the left-right direction, and the valve body 51 opens and closes a valve port 62 provided in the middle of the first straight hole portion 21. In the operating state, the drive valve 50 is in a valve open state away from the valve port 62, and in the non-operating state, the drive valve 50 is addressed to the opening edge of the valve port 62 (that is, the valve seat 62Z) and is in a valve closed state.

The second straight hole portion 31 extends from the left surface of the support base 11 to a position closer to the right surface, and the right end portion of the second straight hole portion 31 has the above-mentioned gas phase outflow port 14 extending to the rear surface of the support base 11. Communicating. The intermediate portion of the second straight hole portion 31 is connected to the inner portion of the cylindrical body 12A of the gas-liquid separation chamber 12 by a communication hole 32. The left end of the second straight hole 31 is closed by a support cap 44 that supports the compression coil spring 42 provided in the differential pressure valve 40. The valve body 41 provided in the differential pressure valve 40 opens and closes the valve port 43 provided in the middle of the second straight hole 31 from the left side. The valve body 41 is urged to a closed state by a compression coil spring 42.

The left side portion of the first straight hole portion 21 and the left end portion of the second straight hole portion 31 are communicated with each other by an internal pressure introduction path 19.

As shown in FIG. 4, the support base 11 is provided with a bottom wall 39 for partitioning between the gas-liquid separation chamber 12 and the first straight hole portion 21. A communication hole 34 that extends in the vertical direction and connects the gas-liquid separation chamber 12 and the first straight hole portion 21 penetrates through the bottom wall 39. Specifically, a diameter-expanded portion 23 is provided in a portion of the first straight hole portion 21 that is arranged directly below the gas-liquid separation chamber 12. Then, the lower end of the communication hole 34 is opened in the enlarged diameter portion 23.

Here, a cylindrical heat insulating member 60 is fitted in the first straight hole portion 21 (see FIG. 6). The heat insulating member 60 is made of a material having a thermoelectricity lower than that of the support base 11, and in the example of the present embodiment, it is an injection molded product of resin. The heat insulating member 60 is fitted to the left end of the first straight hole portion 21, and an axially intermediate portion of the heat insulating member 60 is sealed with an O-ring 60R. The right end portion of the heat insulating member 60 is arranged in the diameter-expanded portion 23 and is arranged with a gap from the inner surface of the diameter-expanded portion 23. The right end opening of the heat insulating member 60 constitutes a valve opening 62 that is opened and closed by the drive valve 50. The opening edge of the valve port 62 in the heat insulating member 60 is a valve seat 62Z to which the valve body 51 of the drive valve 50 abuts. The left end surface of the heat insulating member 60 is abutted against the left end of the first straight hole portion 21, and the engaging protrusion 64 provided on a part of the left end surface of the heat insulating member 60 in the circumferential direction is formed by the first straight hole portion 21. The engagement recess 24 (corresponding to the "positioning portion" described in the claims) at the left end of the heat insulating member 60 is concavely engaged with the heat insulating member 60 in the axial direction. As a result, the heat insulating member 60 is prevented from rotating with respect to the support base 11. Specifically, the heat insulating member 60 is stopped at a position where the through hole 67 penetrating the outer peripheral wall of the heat insulating member 60 and the liquid phase outflow port 15 communicate with each other. At this position, the internal pressure introduction path 19 is arranged on the extension of the discharge hole 65, which will be described later, which penetrates the outer peripheral wall of the heat insulating member 60 so as to be orthogonal to the through hole 67. In the present embodiment, the engaging protrusion 64 and the engaging recess 24 correspond to the "first positioning engaging portion" described in the claims.

As shown in FIGS. 4 and 7, the heat insulating member 60 is formed with an orifice 61 that communicates inside and outside in the radial direction. The orifice 61 is narrowed toward the inside of the heat insulating member 60. Specifically, the orifice 61 is provided at the right end portion of the heat insulating member 60, which is arranged with a gap between the inner surface of the first straight hole portion 21 and the inner surface of the enlarged diameter portion 23. The orifice 61 extends upward from a portion arranged on the lower side of the outer peripheral surface of the heat insulating member 60. Further, the orifice 61 is arranged at a position of the first straight hole 21 separated from the confluence with the gas-liquid separation chamber 12 in the axial direction of the first straight hole 21 (on the left side shown in FIG. 4). .. In the present embodiment, the orifice 61 is orthogonal to the axial direction of the heat insulating member 60, but may be inclined. For example, the orifice 61 may extend closer to the inside of the heat insulating member 60 toward the downstream side.

As shown in FIG. 7, the upper surface of the bottom wall 39 is provided with a first engaging hole 33A and a second engaging hole 33B in addition to the communication hole 34. An umbrella-shaped cover member 70 is attached to the first engaging hole 33A. Specifically, the umbrella-shaped cover member 70 has an insertion bar 70B hanging from the umbrella portion 70A. The insertion bar 70B is, for example, press-fitted into the second engagement hole 33B. At this time, the umbrella portion 70A is arranged so as to cover the communication hole 34 and the second engagement hole 33B from above.

The second engaging hole 33B faces a portion of the outer peripheral surface of the end portion of the heat insulating member 60 that is opposite to the orifice 61 in the circumferential direction. A regulation bar 72 is inserted into the second engagement hole 33B. The upper end of the regulation bar 72 is in contact with the lower surface of the umbrella portion 70A to restrict movement. The lower end of the regulation bar 72 engages with the engaging recess 63 formed on the outer peripheral surface of the end of the heat insulating member 60 to prevent the heat insulating member 60 from rotating, and also supports the heat insulating member 60 as a support base. It is prevented from coming off with respect to 11 (specifically, the lower base 20B described later). In the present embodiment, the "second positioning engaging portion" described in the claims is configured from the regulation bar 72 and the engaging recess 63.

As shown in FIG. 8, the regulation bar 72 in contact with the heat insulating member 60 is visible in a state where the drive valve 50 is removed from the opening of the first straight hole 21 provided on the right side of the support base 11. It has become. This makes it easy to confirm whether or not the heat insulating member 60 is positioned by the regulation bar 72.

As shown in FIG. 7, the integrated valve 10 is provided with a discharge hole 65 that penetrates in and out of the heat insulating member 60 on the downstream side (left side portion) of the orifice 61. Further, between the outer peripheral surface of the heat insulating member 60 and the inner peripheral surface of the first straight hole portion 21, the upstream side of the O-ring 60R is disconnected, while the liquid phase outflow port 15 and the discharge hole are disconnected. An annular flow path 66 communicating with 65 (corresponding to the "curved flow path" described in the claims) is formed. The annular flow path 66 is connected to the internal pressure introduction path 19. Specifically, as shown in FIG. 6, an annular recess 66U for forming the annular flow path 66 is formed on the outer peripheral surface of the heat insulating member 60. The annular flow path 66 may be C-shaped.

The support base 11 is formed by connecting the upper base 20A and the lower base 20B vertically. The lower base has a substantially rectangular parallelepiped shape, and a drive valve 50 is attached to the right side. As shown in FIG. 2, the liquid phase outflow port 15 described above is open on the front surface of the lower base 20B. Further, as shown in FIG. 3, the upper base 20A has a rectangular block shape in front view, and the above-mentioned gas phase outflow port 14 and inflow port 13 are arranged side by side on the rear surface of the upper base 20A. It is open. Further, the gas-liquid separation chamber 12 is arranged at the boundary between the upper base 20A and the lower base 20B, and the lower end portion of the gas-liquid separation chamber 12 is composed of the upper surface opening 30A of the lower base 20B and the bottom portion of the upper surface opening 30A. Is composed of a bottom wall 39.

In the present embodiment, for example, the heat insulating member 60 is mounted in the lower base 20B before the lower base 20B and the upper base 20A are combined. Specifically, it is inserted from one end opening of the first straight hole portion 21 of the lower base 20B before the drive valve 50 is attached, fitted into the first straight hole portion 21, and engaged with the heat insulating member 60. The protrusion 64 and the engaging recess 24 of the first straight hole 21 engage with each other in a concavo-convex manner. Then, the regulation bar 72 is inserted from the upper surface opening 30A of the lower base 20B into the second engaging hole 33B of the bottom wall 39 and engages with the engaging recess 63 of the heat insulating member 60. After that, the umbrella-shaped cover member 70 is inserted into the first engaging hole 33A and comes into contact with the upper end portion of the regulation bar 72. As a result, the heat insulating member 60 is attached to the lower base 20B.

In the integrated valve 10 of the present embodiment, the differential pressure valve 40 that opens and closes the gas phase outflow port 14 operates as follows. When the heat pump cycle 80 is in the normal heating mode, the valve port 62 is opened when the drive valve 50 is driven to the valve open state, as shown in FIG. In this case, the pressure in the second straight hole 31 passing through the communication hole 32 is different from the pressure of the refrigerant in the first straight hole 21 passing through the internal pressure introduction path 19 (back pressure of the valve body 41). It is considered that the valve body 41 is not strong enough to move the valve body 41 to the valve opening position, and the valve body 41 urged by the compression coil spring 42 is maintained so that the valve opening 43 is in the closed state. Therefore, when the heat pump cycle 80 is in the normal heating mode, the gas phase outflow port 14 of the integrated valve 10 is blocked, and the liquid refrigerant flows out only from the liquid phase outflow port 15. Here, when the heat pump cycle 80 is switched to the special heating mode, the drive valve 50 is driven to the closed state to close the valve port 62 (see FIG. 5). The liquid refrigerant separated in the gas-liquid separation chamber 12 flows down from the gas-liquid separation chamber 12 into the enlarged diameter portion 23 of the first straight hole portion 21, and then passes through the orifice 61 to the inside of the heat insulating member 60. It flows into the part. At this time, the liquid refrigerant is depressurized. Then, the back pressure of the valve body 41 of the differential pressure valve 40 becomes the same as the pressure in the first straight hole portion 21 due to the internal pressure introduction path 19. Then, when the pressure in the communication hole 32 becomes larger than the back pressure of the valve body 41, the valve body 41 opens the valve opening 43 as shown in FIG. As a result, the gaseous refrigerant flows out from the gas phase outflow port 14 and flows into the compressor 81. This constitutes a gas injection cycle. The details of the differential pressure valve 40 are also disclosed in, for example, Japanese Patent Application Laid-Open No. 2017-53591.

In the present embodiment, the inflow port 13, the liquid phase outflow port 15, and the gas phase outflow port 14 are described in the claims as "indoor condenser port", "outdoor evaporator port", and "compressor", respectively. Corresponds to "port". Further, the inflow port 13 constitutes the "first flow path" described in the claims. Further, the communication hole 34, the enlarged diameter portion 23 of the first straight hole portion 21, the inside of the heat insulating member 60, and the outflow port 15 for the liquid phase form the "second flow path" described in the claims. Further, the communication hole 32, the second straight hole portion 31, and the gas phase outflow port 14 form the "third flow path" described in the claims.

In the present disclosure, "parallel" means not only a state of being strictly parallel but also a state of being substantially parallel (for example, a state of being inclined to each other at an angle of 5 degrees or less). Further, "orthogonal" means not only exactly intersecting at 90 degrees but also substantially orthogonal (for example, intersecting at an angle of 85 degrees or more and 95 degrees or less).

The structure of the integrated valve 10 of the present embodiment is as described above. In the present embodiment, since the orifice 61 is formed in the member assembled inside the support base 11, it is possible to facilitate the formation of the orifice 61 as compared with the case where the orifice 61 is directly formed inside the support base 11. It will be possible. In the present embodiment, the member on which the orifice 61 is formed is cylindrical, and the orifice 61 is formed in the radial direction thereof, so that the orifice 61 can be formed more easily.

Further, since the member provided with the orifice 61 is a heat insulating member, the density of the refrigerant passing through the orifice 61 is less likely to change due to external heat, and the flow rate of the refrigerant passing through the orifice 61 can be stabilized. Become. Here, the gas-liquid separated liquid refrigerant does not only contain the completely liquid refrigerant, but may also contain the gaseous refrigerant without being completely separated. In this case, when the slip ratio (the speed of the gas refrigerant / the speed of the liquid refrigerant), which is the speed ratio between the gas refrigerant and the liquid refrigerant in the liquid refrigerant, becomes large, the density of the refrigerant passing through the orifice 61 is affected by the temperature. The flow rate of the refrigerant passing through the orifice 61 is not stable. On the other hand, in the integrated valve 10 of the present embodiment, the orifice 61 penetrates the heat insulating member 60 in the radial direction, so that the liquid refrigerant circulating in the first straight hole 21 enters the orifice 61. When you do, you will change direction. This makes it easier to agitate the gas refrigerant and the liquid refrigerant in the liquid refrigerant, and it is possible to suppress an increase in the slip ratio.

Further, in the present embodiment, the orifice 61 penetrates the heat insulating member 60 from the lower side to the upper side. Therefore, even when the amount of the liquid refrigerant separated in the gas-liquid separation chamber 12 is small, it is possible to facilitate the passage of the liquid refrigerant through the orifice 61 as compared with the configuration in which the orifice 61 is provided in the upper portion of the heat insulating member 60. It will be possible.

[Other Embodiments]
(1) In the above embodiment, the heat insulating member 60 has a cylindrical shape, but the present invention is not limited to this, and the heat insulating member 60 may have a rectangular parallelepiped shape or a block shape such as a rectangular parallelepiped shape. You may.

(2) In the above embodiment, the umbrella-shaped cover member 70 is separate from the regulation bar 72, but may be integrated.

10 Integrated valve 11 Support base 60 Insulation member 61 Orifice 80 Heat pump cycle

Claims (13)

An integrated valve that is incorporated into a heat pump cycle having an indoor condenser, an outdoor evaporator, and a compressor to switch the heat pump cycle between a normal indoor heating mode and a special indoor heating mode.
Support base and
A gas-liquid separation chamber formed on the support base, which takes in the refrigerant, separates the gas and liquid, and discharges the gaseous refrigerant and the liquid refrigerant separately.
A first flow path for taking in the refrigerant, which has a port for an indoor condenser extending from the gas-liquid separation chamber and connected to the indoor condenser at the end, and a first flow path for taking in the refrigerant.
A second flow path for the liquid refrigerant having an outdoor evaporator port extending from the gas-liquid separation chamber and connected to the outdoor evaporator at the end.
A third flow path for the gaseous refrigerant having a compressor port extending from the gas-liquid separation chamber and connected to the input port of the compressor at the end.
It is provided in the middle of the third flow path, and is usually in a valve closed state in which the third flow path is shut off, and in a valve open state in which the third flow path is opened according to the pressure of the second flow path. With a differential pressure valve
A drive valve provided in the middle of the second flow path and driven so as to be in a valve open state in the normal room heating mode and in a valve closed state in the special room heating mode.
A heat insulating member formed of a material having a lower thermal conductivity than the support base, assembled inside the support base, and through which a part of the second flow path penetrates.
An integrated valve including an orifice formed in the heat insulating member and connecting between the upstream side and the downstream side of the valve port which is opened and closed by the drive valve in the second flow path. One end opening of the portion of the second flow path that penetrates the heat insulating member forms a valve opening that is opened and closed by the valve body of the drive valve, and the opening edge of the one end opening is formed by the valve body of the drive valve. The integrated valve according to claim 1, which is a valve seat that comes into contact with the valve seat. The support base is arranged so as to extend laterally below the gas-liquid separation chamber when the integrated valve is used, a part thereof constitutes a part of the second flow path, and one end thereof drives the drive. A first straight hole is formed, which comprises a first valve mounting portion that is closed by a valve support body, and a positioning portion whose other end is closed or reduced in diameter.
The integrated valve according to claim 2, wherein the heat insulating member is fitted in the first straight hole portion and an end portion opposite to the valve seat is positioned by the positioning portion. The heat insulating member has a cylindrical shape and has a tubular shape.
The integrated valve according to claim 3, wherein the orifice is formed so as to communicate between the inner surface and the outer surface of the heat insulating member. The integrated valve according to claim 4, wherein the orifice is arranged at a position of the first straight hole portion separated from the confluence portion with the gas-liquid separation chamber in the axial direction of the first straight hole portion. The integrated valve according to claim 4 or 5, wherein the orifice is arranged so that the refrigerant passes inside and outside the heat insulating member toward the upper side when the integrated valve is used. Any of claims 4 to 6, further comprising a first positioning engaging portion formed on the positioning portion and the heat insulating member and engaging with the heat insulating member in the axial direction to prevent the heat insulating member from rotating. The integrated valve according to claim 1. A communication hole, a first engagement hole, and a second engagement hole that partition the gas-liquid separation chamber and the first straight hole portion and communicate between the gas-liquid separation chamber and the first straight hole portion. A bottom wall with holes and
An insertion bar hangs down from an umbrella portion that covers the communication hole and the second engagement hole from above when the integrated valve is used, and the insertion bar is inserted into the first engagement hole and is inserted into the bottom wall. Umbrella-shaped cover member to be fixed and
Through the second engaging hole, upward movement is restricted by the umbrella portion when the integrated valve is used, and the lower end portion is engaged with the heat insulating member to the drive valve side of the heat insulating member. The integrated valve according to any one of claims 4 to 7, further comprising a movement control bar that regulates the movement of the vehicle. A second positioning engaging portion for preventing the heat insulating member from rotating from a lower end portion of the movement restricting bar and a recess formed in the heat insulating member and engaged with the lower end portion of the movement restricting bar. 8. The integrated valve according to 8. The integrated valve according to claim 8 or 9, wherein the lower end portion of the movement restriction bar becomes visible when the support body of the drive valve is removed from the first valve mounting portion. The support base is formed with a second straight hole portion that extends parallel to the first straight hole portion on the upper side of the gas-liquid separation chamber when the integrated valve is used.
Of the second straight hole portion, one end side of the gas-liquid separation chamber on the side of the first valve mounting portion constitutes at least a part of the third flow path.
The integrated valve according to any one of claims 3 to 10, wherein the other end of the second straight hole is closed by a support cap for supporting the urging member provided in the differential pressure valve. .. A discharge hole that penetrates inside and outside the portion of the heat insulating member on the downstream side of the orifice.
The outdoor evaporator port and the outdoor evaporator port formed between the outer peripheral surface of the heat insulating member and the inner peripheral surface of the first straight hole portion and disconnected from the upstream side portion of the second flow path from the valve opening. A curved flow path that communicates with the discharge hole and forms a part of the second flow path,
The integrated valve according to claim 1, further comprising an internal pressure introduction path for communicating with the curved flow path and taking in the internal pressure of the second flow path into the differential pressure valve. The discharge hole is arranged so as to face upward when the integrated valve is used, and penetrates from the inside to the outside of the heat insulating member.
The internal pressure introduction path is arranged so as to extend upward from the curved flow path when the integrated valve is used.
The integrated valve according to claim 12, wherein the outdoor evaporator port is arranged on the side of the curved flow path.

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