WO2021084740A1

WO2021084740A1 - Integrated valve

Info

Publication number: WO2021084740A1
Application number: PCT/JP2019/043069
Authority: WO
Inventors: 和宏金森; 坂井　孝行
Original assignee: 太平洋工業株式会社
Priority date: 2019-11-01
Filing date: 2019-11-01
Publication date: 2021-05-06
Also published as: JP7157809B2; JPWO2021084740A1

Abstract

[Problem] To improve thermal efficiency. [Solution] Provided is an integrated valve (10) in which an upper body (11A) is formed by fitting a double-cylinder component (65) having a gas-liquid separation chamber (12) inside in the upper support base (20A). The double-cylinder component (65) is a one-piece foam molded product of resin and has a lower thermal conductivity than the upper support base (20A) and a lower support base (20B). The double-cylinder component (65) has: an outer cylinder (66) that abuts on the inner peripheral surfaces of an upper cylinder receiving portion (25) and a lower cylinder receiving portion (26); an inner cylinder (67) that is disposed inside the outer cylinder (66); and an annular plate (68) that connects between the outer cylinder (66) and the inner cylinder (67).

Description

Integrated valve

The present disclosure is incorporated in a heat pump cycle having an indoor condenser, an outdoor evaporator, and a compressor, and the gas-liquid mixed refrigerant flowing from the indoor condenser is swirled along the inner peripheral surface of the gas-liquid separation chamber to separate the gas and liquid. The present invention relates to an integrated valve capable of switching between a first state in which the separated liquid phase refrigerant flows out to the outdoor evaporator and a second state in which the separated vapor phase refrigerant flows out to the compressor.

Conventionally, as this type of integrated valve, a gas-phase refrigerant outflow pipe is integrally formed on a metal base, which is arranged inside the gas-liquid separation chamber and allows the separated gas-phase refrigerant to flow out of the gas-liquid separation chamber. Is known (see, for example, Patent Document 1).

Japanese Unexamined Patent Publication No. 2013-92355 (paragraphs [0122] to [0123], FIG. 4)

The above-mentioned conventional integrated valve is required to improve thermal efficiency.

The integrated valve of the present disclosure is incorporated in a heat pump cycle having an indoor condenser, an outdoor evaporator and a compressor, and the gas-liquid mixed refrigerant flowing from the indoor condenser is swirled along the inner peripheral surface of the gas-liquid separation chamber. In an integrated valve that can be switched between a first state in which the liquid-separated and separated liquid-phase refrigerant flows out to the outdoor evaporator and a second state in which the separated vapor-phase refrigerant flows out to the compressor. , The gas-phase refrigerant outflow pipe arranged inside the gas-liquid separation chamber and causing the separated gas-phase refrigerant to flow out from the gas-liquid separation chamber, and the gas-phase refrigerant outflow pipe, which are tubular. The outer cylinder portion whose peripheral surface forms the inner peripheral surface of the gas-liquid separation chamber and the communication plate portion that connects the gas phase refrigerant outflow pipe and the outer cylinder portion are integrally molded with resin. It is an integrated valve equipped with a heavy cylinder component.

According to the integrated valve of claim 1, since the outer cylinder portion surrounding the gas-liquid separation chamber and the gas-phase refrigerant outflow pipe are molded of resin, external heat is less likely to be transmitted and thermal efficiency is improved.

Conceptual diagram of a heat pump cycle in which the integrated valve according to the first embodiment is incorporated. Front perspective view of the integrated valve Rear view of integrated valve Positive cross section of integrated valve Planosection view near the shutter member Positive cross section of integrated valve Perspective view of double cylinder member Regular cross-sectional view of double cylinder member Planosection of integrated valve Lower perspective view of double cylinder member Positive sectional view of the integrated valve according to the second embodiment Perspective view of shutter member Front view of shutter member Regular cross-sectional view near the shutter member Perspective view of the double cylinder member according to the modified example Regular cross-sectional view of the double cylinder member according to the modified example Lower perspective view of the double cylinder member according to the modified example Regular cross-sectional view of the double cylinder member according to the modified example A cross-sectional view taken along the line in FIG. Regular cross-sectional view of the double cylinder member according to the modified example BB sectional view in FIG. 20 Lower perspective view of the double cylinder member according to the modified example Positive cross-sectional view of the integrated valve according to the modified example Regular cross-sectional view near the shutter member of the integrated valve according to the modified example Positive cross-sectional view of the integrated valve according to the modified example

[First Embodiment]
Hereinafter, the integrated valve 10 of the present embodiment will be described with reference to FIGS. 1 to 10. 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 includes a compressor 81 and an outdoor heat exchanger 83 (outdoor evaporator) arranged outside the vehicle interior (for example, inside the bonnet), and an indoor condenser 82 and an indoor evaporator 84 arranged inside the vehicle interior (inside the air conditioning unit). It is possible to switch between cooling mode and heating mode.

The compressor 81 sucks in the refrigerant, compresses it, and discharges it. The compressor 81 includes a low-pressure input port 81A for sucking low-temperature low-pressure refrigerant, an intermediate pressure input port 81B for merging the sucked refrigerant with the refrigerant in the process of compressing the sucked refrigerant from low-temperature low-pressure to high-temperature high-pressure, and a high-temperature and high-pressure compressed refrigerant. An outflow output port 81C is provided.

An indoor capacitor 82 is connected to the output port 81C of the compressor 81. The indoor condenser 82 functions as a radiator that dissipates high-temperature and high-pressure refrigerant discharged from the output port 81C of the compressor 81 (warms the interior of the vehicle). In the cooling mode, the interior condenser 82 is covered with, for example, a cover so that the interior of the vehicle cannot be warmed.

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 80 is in the heating mode, while as a radiator that dissipates the refrigerant when the heat pump cycle 80 is in the cooling mode. Function.

The low pressure input port 81A of the compressor 81 is connected to the output port of the outdoor heat exchanger 83 via the on-off valve 86. Further, an expansion valve 85 and an indoor evaporator 84 are arranged in parallel with the on-off valve 86 between the output port of the outdoor heat exchanger 83 and the low-voltage input port 81A of the compressor 81. When the heat pump cycle 80 is in the heating mode, the on-off valve 86 is controlled to be in the open state and the expansion valve 85 is closed, and the refrigerant from the outdoor heat exchanger 83 flows directly into the compressor 81 without flowing into the indoor evaporator 84. To do. On the other hand, when the heat pump cycle 80 is in the cooling mode, the on-off valve 86 is controlled to be in the closed state, the expansion valve 85 is opened, and the refrigerant from the outdoor heat exchanger 83 flows into the indoor evaporator 84. The indoor evaporator 84 absorbs heat from the air inside the vehicle interior (cools the vehicle interior) and evaporates the refrigerant that has flowed in from the outdoor heat exchanger 83.

As shown in FIG. 1, the integrated valve 10 is separated by an inflow port 13 into which the refrigerant flows, a gas-liquid separation chamber 12 capable of separating the refrigerant flowing from the inflow port 13, and a gas-liquid separation chamber 12. It has a gas phase outflow port 14 for flowing out the gas phase refrigerant and a liquid phase outflow port 15 for flowing out the liquid phase refrigerant separated in the gas-liquid separation chamber 12. The inflow port 13 is connected to the output port of the indoor capacitor 82 via an expansion valve 87, the gas phase outflow port 14 is connected to the intermediate pressure input port 81B of the compressor 81, and the liquid phase outflow port 15 is It is connected to the input port of the outdoor heat exchanger 83. Further, the integrated valve 10 is provided with a drive valve 50 (electromagnetic valve in the example of the present embodiment) and an orifice 61 in parallel between the gas-liquid separation chamber 12 and the liquid phase outflow port 15, and gas-liquid separation is performed. A differential pressure valve 40 is provided between the chamber 12 and the gas phase outflow port 14, and the gas phase outflow port 14 can be opened and closed by opening and closing the drive valve 50 (specifically, the drive valve). When 50 is opened, the gas phase outflow port 14 is closed, and when the drive valve 50 is closed, the gas phase outflow port 14 is opened). The opening / closing control of the integrated valve 10 will be described in detail later.

In the heat pump cycle 80, a normal heating mode and a special heating mode are provided as heating modes. In the normal heating mode, the drive valve 50 of the integrated valve 10 is opened, and the gas phase outflow port 14 of the integrated valve 10 is closed (see FIG. 1 (A)). On the other hand, in the special heating mode, the drive valve 50 of the integrated valve is closed, and the gas phase outflow port 14 of the integrated valve 10 is opened. 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 (see FIG. 1B). 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.

In detail, 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 (the refrigerant cannot be sufficiently evaporated). 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. 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 refrigerant in the gas phase 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 possible to suppress a decrease in the discharge pressure of the refrigerant from the compressor 81. As a result, the heating performance can be improved.

Next, the details of the integrated valve 10 will be described. As shown in FIGS. 2 to 4, the integrated valve 10 includes a plurality of flow paths inside the vertically elongated body 11. The integrated valve 10 is arranged so that the longitudinal direction of the body 11 is 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 description, the vertical direction when the integrated valve 10 is used is referred to as the vertical direction of the integrated valve 10. Further, the left-right direction in FIG. 4 is the left-right direction of the integrated valve 10, the front side of the paper surface in FIG. 4 is the front side, and the back side of the paper surface is the rear side.

As shown in FIG. 4, the body 11 is formed by connecting the upper body 11A and the lower body 11B vertically. The upper body 11A is made of metal and has a block-shaped upper support base 20A having a quadrangular front view, and the lower body 11B is made of metal and has a substantially rectangular parallelepiped lower support base 20B. A gas-liquid separation chamber 12 is provided between the upper body 11A and the lower body 11B. 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. An inflow port 13 for communicating the outside of the integrated valve 10 and the gas-liquid separation chamber 12 is opened in the upper right portion on the rear side of the inner peripheral surface 12B of the gas-liquid separation chamber 12.

The gas-liquid separation chamber 12 is of a centrifugal separation type, and the refrigerant of the gas-liquid mixture flowing from the indoor condenser 82 through the inflow port 13 swirls along the inner peripheral surface 12B of the gas-liquid separation chamber 12. The centrifugal force generated by this swirl separates the gas phase refrigerant and the liquid phase refrigerant. The separated gas-phase refrigerant passes through the inside of the cylindrical body 12A and goes upward, and the separated liquid-phase refrigerant travels downward along the inner peripheral surface 12B of 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 provided on the lower side and the upper side of the gas-liquid separation chamber 12 in the body 11. The first straight hole portion 21 has a circular cross section and extends from the right surface to the left surface side position of the lower support base 20B in the lower body 11B. Further, the first straight hole portion 21 has a reduced diameter portion 21A whose diameter is gradually reduced toward the left from the right end opening and a uniform diameter after being tapered from the end portion of the reduced diameter portion 21A. It has an inflow portion 21B that extends to the left and then has a tapered diameter, and an outflow portion 21C that extends from the end of the inflow portion 21B to the left end of the first straight hole 21 with a uniform diameter. ..

A support body 53 of a drive valve 50 that moves directly in the first straight hole 21 is attached to the right surface of the lower support base 20B, and the support body 53 closes the right end opening of the first straight hole 21. ing. One part of the support body 53 is positioned by being received by the reduced diameter portion 21A of the first straight hole portion 21. The support body 53 and the reduced diameter portion 21A of the first straight hole portion 21 are sealed by an O-ring 53R. The drive valve 50 opens and closes the valve port 62, which will be described later, by the valve body 51 provided at the tip. In the non-operating state, the drive valve 50 is in a valve-opened state away from the valve opening 62, and in the operating state, the drive valve 50 is addressed to the opening edge of the valve opening 62 (that is, the valve seat 62Z) and is closed.

A cylindrical heat insulating member 60 made of a material (for example, resin) having a lower thermoelectricity than the upper and

lower support bases

20A and 20B is fitted in the left portion of the first straight hole portion 21. .. The lower support base 20B and the heat insulating member 60 are sealed by an O-ring 60R arranged in the middle of the heat insulating member 60 in the axial direction. The right end portion of the heat insulating member 60 is arranged in the inflow portion 21B and is arranged with a gap from the inner surface of the inflow portion 21B. 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 inside of the first straight hole portion 21 and the heat insulating member 60 is a liquid phase refrigerant flow path 21R.

The liquid phase outflow port 15 described above is formed so as to penetrate the lower support base 20B and the heat insulating member 60, and communicates the outside of the integrated valve 10 with the liquid phase refrigerant flow path 21R (inside the heat insulating member 60). .. In the heat insulating member 60, the engaging protrusion 64 provided in a part of the left end surface in the circumferential direction engages with the engaging recess 24 formed at the left end of the first straight hole portion 21 in an uneven manner. , It is prevented from rotating with respect to the body 11. Further, the movement of the heat insulating member 60 to the right is restricted by engaging the regulating bar 72 mounted on the partition wall 39, which will be described later, with the engaging recess 63 formed on the outer peripheral surface of the heat insulating member 60. There is.

An orifice 61 extending in the radial direction and communicating the inside of the heat insulating member 60 and the inflow portion 21B of the first straight hole 21 is formed in the lower part of the right end of the heat insulating member 60. The orifice 61 is narrowed toward the inside of the heat insulating member 60.

As shown in FIG. 4, the lower support base 20B of the lower body 11B is provided with a partition wall 39 for partitioning between the gas-liquid separation chamber 12 and the first straight hole portion 21. A communication hole 34 extending in the vertical direction and connecting the gas-liquid separation chamber 12 and the first straight hole portion 21 is formed through the partition wall 39. Specifically, an inflow portion 21B is provided in a portion of the first straight hole portion 21 arranged directly below the gas-liquid separation chamber 12. Then, the lower end of the communication hole 34 is opened in the inflow portion 21B. The communication holes 34 are formed at two positions of the outer edge of the partition wall 39 facing each other with the center in between (see FIG. 5).

As shown in FIGS. 4 and 5, an upwardly projecting protruding portion 39T is formed in the central portion on the upper surface of the partition wall 39, and the protruding portion 39T has a first engagement extending downward from the upper surface. Hole 39A is provided. A shutter member 70 is attached to the first engaging hole 39A. Specifically, the shutter member 70 has an insertion bar 70B hanging from the center of the lower surface of the disc-shaped shutter portion 70A. The insertion bar 70B is press-fitted into the first engagement hole 39A. The shutter portion 70A covers a part of the two communication holes 34 (the central portion of the partition wall 39) from above. Further, the side surface of the shutter portion 70A is tapered. The partition wall 39 is formed with a second engagement hole 39B that is displaced from the first engagement hole 39A in the horizontal direction and penetrates the partition wall 39 at a position covered by the shutter portion 70A from above. 2 The above-mentioned regulation bar 72 is attached to the engagement hole 39B.

As shown in FIG. 4, the second straight hole portion 31 above the gas-liquid separation chamber 12 extends from the left surface of the upper support base 20A of the upper body 11A to a position closer to the right surface. The above-mentioned gas phase outflow port 14 is formed through the rear surface of the upper support base 20A from the rear surface to the second straight hole portion 31 behind the right end portion of the upper support base 20A, and the gas phase outflow port 14 is formed. , The outside of the integrated valve 10 and the right end of the second straight hole 31 are communicated with each other. 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. Further, the portion of the second straight hole portion 31 near the gas phase outflow port 14 has a stepped diameter reduced from the left portion thereof, and an annular recess 31U is formed in the stepped portion 31D between them. Has been done.

A differential pressure valve 40 capable of opening and closing the flow path between the cylindrical body 12A and the gas phase outflow port 14 is attached to the second straight hole portion 31. Specifically, the left end portion of the second straight hole portion 31 is closed by the support cap 44, and the differential pressure valve 40 is arranged on the right side of the support cap 44 with the compression coil spring 42 interposed therebetween. The differential pressure valve 40 is urged toward the stepped portion 31D by the compression coil spring 42, and the valve body 41 provided in the differential pressure valve 40 always closes the valve port 43 at the inner edge of the stepped portion 31D from the left side. There is. Further, there is a gap between the differential pressure valve 40 and the recess 31U of the stepped portion 31D, and further, the differential pressure valve 40 does not block between the recess 31U and the communication hole 32 even in the valve closed state. It is configured in. As a result, the differential pressure valve 40 can receive the pressure in the communication hole 32 (that is, the pressure in the cylindrical body 12A of the gas-liquid separation chamber 12). Further, as shown in the figure, the left portion of the first straight hole portion 21 (and the heat insulating member 60) and the left portion of the second straight hole portion 31 are communicated with each other by the internal pressure introduction path 19. An introduction path member 19A for sealing between the upper support base 20A and the lower support base 20B is arranged in the middle of the internal pressure introduction path 19, and the introduction path member 19A and the upper and lower sides are arranged. The support bases 20A and 20B are sealed by an O-ring 19R.

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 drive valve 50 is opened and the valve port 62 is opened, as shown in FIG. In this case, the pressure in the recess 31U passing through the communication hole 32 is relative to the pressure of the refrigerant (back pressure of the valve body 41) in the first straight hole 21 (in the heat insulating member 60) passing through the internal pressure introduction path 19. Is not considered to be 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.

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. 6). When the refrigerant flows into the gas-liquid separation chamber 12 in this state, the liquid-phase refrigerant separated in the gas-liquid separation chamber 12 flows down from the gas-liquid separation chamber 12 into the inflow portion 21B of the first straight hole portion 21. , Passes through the orifice 61 without passing through the valve port 62, and flows into the inner portion of the heat insulating member 60. At this time, the liquid phase refrigerant is depressurized by flowing from the small-diameter orifice 61 into the large-diameter heat insulating member 60. Due to the internal pressure introduction path 19, 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. 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 gas phase refrigerant flows out from the gas phase outflow port 14 and flows into the compressor 81. This constitutes a gas injection cycle.

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 tilted at an angle of 5 degrees or less).

By the way, in the integrated valve 10 of the present embodiment, as shown in FIG. 4, the upper body 11A is formed by assembling the double cylinder component 65 having the gas-liquid separation chamber 12 inside to the above-mentioned upper support base 20A. .. Specifically, the upper support base 20A is formed with the upper cylinder receiving portion 25 recessed upward from the lower surface, while the lower support base 20B is formed with the lower cylinder receiving portion recessed downward from the upper surface. The portion 26 is formed. The cross-sectional shapes of the upper cylinder receiving portion 25 and the lower cylinder receiving portion 26 are both circular and the same, and the inner peripheral surfaces of the upper cylinder receiving portion 25 and the lower cylinder receiving portion 26 are flush with each other. A communication hole 32 is opened on the ceiling surface of the upper cylinder receiving portion 25. The lower end of the communication hole 32 is a diameter-expanded portion 32A whose diameter is stepped from the upper portion thereof. Further, the upper surface of the partition wall 39 described above constitutes the lower surface of the lower cylinder receiving portion 26.

The double cylinder component 65 shown in FIG. 7 is fitted inside the upper cylinder receiving portion 25 and the lower cylinder receiving portion 26. The double-cylinder component 65 is an integrally foam-molded product of resin (for example, PPS), and has a lower thermal conductivity than the upper support base 20A and the lower support base 20B (see FIG. 4). As shown in FIGS. 7 and 8, the double cylinder component 65 is arranged inside the outer cylinder portion 66 and the outer cylinder portion 66 that abuts on the inner peripheral surfaces of the upper cylinder receiving portion 25 and the lower cylinder receiving portion 26. It has an inner cylinder portion 67 and a ring plate portion 68 that connects the outer cylinder portion 66 and the inner cylinder portion 67.

As shown in FIGS. 4 and 8, the outer cylinder portion 66 extends from the ceiling surface of the upper cylinder receiving portion 25 to the bottom surface of the lower cylinder receiving portion 26 (upper surface of the partition wall 39). A tapered portion 66A corresponding to the tapered side surface of the shutter portion 70A is formed at a position near the lower end of the outer cylinder portion 66, and the inner diameter of the lower portion of the outer cylinder portion 66 of the tapered portion 66A is the outer cylinder portion 66. Of these, it is larger than the inner diameter of the upper portion of the tapered portion 66A. Further, on the outer peripheral surface of the outer cylinder portion 66, two grooves 66M to which two O-rings 66R for sealing between the upper support base 20A and the lower support base 20B are formed are formed.

The inner cylinder portion 67 extends from a position above the upper end of the outer cylinder portion 66 to a position approximately one-third above the axial length of the outer cylinder portion 66 from the lower end of the outer cylinder portion 66, and the lower end opening thereof. Is facing the shutter portion 70A from above. When viewed from below, the entire lower end opening of the inner cylinder portion 67 is covered by the shutter portion 70A. The annular plate portion 68 communicates between the upper end of the outer cylinder portion 66 and the position near the upper end of the inner cylinder portion 67, and is in contact with the ceiling surface of the upper cylinder receiving portion 25. The portion of the inner cylinder portion 67 above the annular plate portion 68 is received by the diameter-expanded portion 32A of the communication hole 32 of the upper cylinder receiving portion 25. Further, the portion of the inner cylinder portion 67 below the annular plate portion 68 forms the above-mentioned cylindrical body 12A.

As shown in FIGS. 3 and 9, in the integrated valve 10 of the present embodiment, the inflow port 13 is formed through the base penetrating portion 13A formed through the upper support base 20A and the outer cylinder portion 66 of the double cylinder component 65. It is composed of a cylinder penetrating portion 13B provided. The base penetrating portion 13A of the upper support base 20A has a circular cross section, and its opening edge is formed in a tapered shape extending outward. Note that FIG. 9 is a view of the planosection of the integrated valve 10 as viewed from below. In the present disclosure, the term "circular" includes not only a perfect circle but also a shape slightly distorted from the perfect circle.

Next, the cylinder penetrating portion 13B of the double cylinder component 65 will be described in detail. As shown in FIG. 10, an inflow guide protrusion 69 projecting inward from the inner peripheral surface of the outer cylinder 66 is integrally formed on the upper portion of the outer cylinder 66, and the inflow guide protrusion 69 and the outer cylinder are integrally formed. A cylinder penetrating portion 13B is provided so as to penetrate the portion 66. As shown in FIGS. 8 to 10, the inflow guide protrusion 69 is formed over a range from the lower surface of the annular plate portion 68 to the height near the upper groove 66M, and is formed on the inner circumference of the outer cylinder portion 66. Of the surfaces, the first surface 69A extending to the left from the position slightly left rear of the rightmost portion, and the inner circumference of the outer cylinder portion 66 extending from the left end of the first surface 69A while curving to the left rear. It has a second surface 69B that communicates with the surface, and a third surface 69C that connects the lower ends of the first surface 69A and the second surface 69B and the inner peripheral surface of the outer cylinder portion 66. The second surface 69B extends from the vicinity of the rear end portion of the inner peripheral surface of the outer cylinder portion 66 to the left end of the first surface 69A while increasing the curvature. A gap of substantially the same length as the width of the first surface 69A in the left-right direction is provided between the first surface 69A and the inner cylinder portion 67.

As shown in FIG. 9, the cylinder penetrating portion 13B extends in the front-rear direction between the first surface 69A of the inflow guide protrusion 69 and the outer peripheral surface of the outer cylinder portion 66. As shown in FIGS. 8 and 9, the cross-sectional shape of the cylinder penetrating portion 13B is an oval shape, and the cylinder penetrating portion 13B has a first facing surface 13B1 and a second facing surfaces facing each other in the width direction (left-right direction). It has a facing surface 13B2. As shown in FIG. 9, in the cross section of the integrated valve 10, the first facing surface 13B1 is slightly to the left of the fictitious tangent line L (tangent line extending in the front-rear direction) passing through the rightmost end of the inner circumference of the outer cylinder portion 66. It is located and extends parallel to the fictitious tangent L from the position near the right end of the first surface 69A. The second facing surface 13B2 extends parallel to the first facing surface 13B1 from a position near the left end of the first surface 69A. Further, the portion of the second facing surface 13B2 that protrudes inward from the inner peripheral surface of the outer cylinder portion 66 corresponds to the "inflow guide portion 69R" in the claims. As shown in FIGS. 7 and 8, the cross-sectional shape of the cylinder penetrating portion 13B is an oval shape. Further, as shown in FIG. 3, in the cylinder penetrating portion 13B, the entire opening edge is exposed by the base penetrating portion 13A when viewed from the outside.

This is the above for the structure of the integrated valve 10 of this embodiment. Next, the action and effect of the integrated valve 10 will be described. According to the integrated valve 10 of the present embodiment, the outer cylinder portion 66 having the inner peripheral surface 12B of the gas-liquid separation chamber 12 and the cylindrical body 12A through which the refrigerant of the gas phase passes are formed of resin, so that gas-liquid mixing is performed. When the refrigerant of the gas-liquid separation chamber 12 swirls around the inner peripheral surface 12B of the gas-liquid separation chamber 12, when the refrigerant of the liquid phase travels through the inner peripheral surface 12B of the gas-liquid separation chamber 12, and when the refrigerant of the gas phase passes through the cylindrical body 12A. In addition, it becomes difficult to transmit to the outside through the upper support base 20A and the lower support base 20B, and the thermal efficiency is improved. In particular, when the upper support base 20A and the lower support base 20B are made of metal as in the present embodiment, the effect becomes more remarkable.

Further, the first facing surface 13B1 of the cylinder penetrating portion 13B, which constitutes a part of the inflow port 13 and allows the gas-liquid mixed refrigerant to flow into the gas-liquid separation chamber 12, is near the tangent line of the inner peripheral surface 12B of the gas-liquid separation chamber 12. In addition, since it extends parallel to the tangent line, it is possible to make it easier for the inflowing refrigerant to follow the inner peripheral surface 12B of the gas-liquid separation chamber 12. Further, since the cross-sectional shape of the cylinder penetrating portion 13B is oval, the width in the radial direction becomes small, and the refrigerant can be easily applied along the inner peripheral surface 12B of the gas-liquid separation chamber 12. Flow rate can be secured. Further, by forming the inflow port 13 from the cylinder penetrating portion 13B and the base penetrating portion 13A, the hole (base penetrating portion 13A) formed in the metal upper support base 20A can be made circular in cross section. It is possible to prevent the occurrence of burrs rather than making the cross section oval.

Further, in the integrated valve 10 of the present embodiment, the cylinder penetrating portion 13B of the outer cylinder portion 66 is provided with an inflow guide portion 69R protruding inward from the inner peripheral surface 12B of the gas-liquid separation chamber 12, so that the cylinder penetrating portion 69R is provided. The inner peripheral surface 12B of the gas-liquid separation chamber 12 makes it easier for the refrigerant flowing in from the portion 13B to follow. Further, since the second surface 69B of the inflow guide protrusion 69 is curved, the refrigerant swirls more than the configuration in which the space between the inflow guide protrusion 69 and the inner peripheral surface 12B of the gas-liquid separation chamber 12 is angular. It is hard to get in the way. It should be noted that the liquid-phase refrigerant is generally captured on the inner peripheral surface until the gas-liquid mixed refrigerant flows in from the inflow port 13 and makes one round (the amount of protrusion of the inflow guide protrusion and the length in the vertical direction). Etc.).

[Second Embodiment]
11 to 14 show the integrated valve 10W of the second embodiment. As shown in FIG. 10, the integrated valve 10W of the present embodiment has a different configuration around the shutter member from the integrated valve 10 of the first embodiment. Hereinafter, the parts having the same configuration as that of the first embodiment are designated by the same reference numerals, the description thereof will be omitted, and only the different points will be described.

As shown in FIG. 12, the shutter member 70W of the present embodiment is radially arranged (at a position where the outer circumference of the shutter portion 70A is divided into three equal parts) on the disc-shaped shutter portion 70A and the outer edge portion of the shutter portion 70A. It is provided with three legs 70C and the like. As shown in FIG. 13, the leg portion 70C has a strip-shaped shape, and the first band portion 70D extending downward from the outer edge of the shutter portion 70A while extending outward, and the U from the end of the first band portion 70D. The second band 70E, which is folded back in a shape and extends upward while facing outward, and one or two sheets below the shutter 70A, bend horizontally outward from the second band 70E. It has a third band portion 70F extending horizontally.

As shown in FIG. 11, the shutter member 70W is sandwiched between the upper body 11A and the lower body 11B. The details will be described below. The integrated valve 10W of the present embodiment does not have the double cylinder component 65 of the first embodiment, and has a first recess 20F recessed upward from the lower surface and a first recess 20F in the upper support base 20A of the upper body 11A. A cylindrical portion 20G protruding downward from the opening edge of the recess 20F is formed, while a second recess 20H recessed downward from the upper surface is formed on the lower support base 20B of the lower body 11B to support the upper side. By fitting the cylindrical portion 20G of the base 20A into the second recess 20H of the lower support base 20B, a gas-liquid separation chamber 12 is formed inside the cylindrical portion 20G.

There is a gap between the lower end of the cylindrical portion 20G and the bottom surface (upper surface of the partition wall 39) of the second recess 20H of the lower support base 20B, and the leg portion 70C of the shutter member 70W is arranged in this gap. .. At this time, as shown in FIG. 14, the folded-back portion 70G between the first band portion 70D and the second band portion 70E in the leg portion 70C abuts on the bottom surface of the second recess 20H of the lower support base 20B, and the second When the three-band portion 70F comes into contact with the lower end of the cylindrical portion 20G, the shutter member 70W is prevented from coming off in the vertical direction. Further, since the leg portion 70C has a shape in which the strip plate is bent, the shutter portion 70A is elastically deformed in the horizontal direction, and the movement and rotation in the horizontal direction are restricted.

Further, in the above embodiment, two communication holes 34 are provided avoiding the insertion bar 70B of the shutter member 70, but in the integrated valve 10W of the present embodiment, one communication hole 34 is provided on the central axis of the gas-liquid separation chamber 12. The entire opening of the communication hole 34 faces the shutter portion 70A from below. That is, the entire opening of the communication hole 34 is covered with the shutter portion 70A from above. Further, similarly to the first embodiment, the entire lower end opening of the gas-liquid separation chamber 12 also faces the shutter portion 70A from above. The gas-liquid separation chamber 12 of the present embodiment is molded of resin, aluminum, or the like, and is caulked and fixed to the upper support base 20A.

This completes the configuration of the integrated valve 10W of this embodiment. Next, the action and effect of the integrated valve 10W will be described. According to the integrated valve 10W of the present embodiment, the shutter member 70W is sandwiched between the upper body 11A and the lower body 11B, so that the dimensional tolerance is larger than that in the conventional case in which the shutter member is press-fitted. And easy to process. Further, since the shutter member 70W can be assembled by mounting the shutter member 70W in the second recess 20H of the lower support base 20B and then attaching the upper support base 20A from above, the shutter member 70W can be easily assembled. become. Further, since the outer edge portion of the shutter member 70W is held, the communication hole 34 can be arranged in the center, and the entire opening of the communication hole 34 can be covered by the shutter portion 70A, and the inside of the gas-liquid separation chamber 12 can be covered. (In particular, the lower end of the cylindrical body 12A) can be made less likely to get dirty.

[Other Embodiments]
(1) In the first embodiment, as shown in FIGS. 15 to 17, a plurality of straightening vanes 13B3 arranged in the longitudinal direction may be provided in the cylinder penetrating portion 13B.

(2) Further, as shown in FIGS. 18 and 19, the straightening vane 13B3 may be configured to be inclined downward as it goes inward. In this case, the refrigerant can be smoothly guided downward while swirling. In the examples shown in FIGS. 18 and 19, the cylinder penetrating portion 13B itself is also inclined, and the refrigerant can be guided downward more smoothly. The cylinder penetrating portion 13B may extend horizontally.

(3) Further, as shown in FIGS. 20 to 22, the inflow guide protrusion 69 may have a configuration in which the amount of protrusion decreases as it goes downward. In this case, it is possible to prevent the refrigerant flowing from the cylinder penetrating portion 13B and swirling from being separated from the inner peripheral surface 12B of the gas-liquid separation chamber 12 by the inflow guide protrusion 69 and moving inward.

(4) In the first embodiment, as shown in FIG. 23, the double cylinder component 65 is provided with a rotation restricting protrusion 65T, and the upper support base 20A is provided with a receiving recess 20U for receiving the rotation regulating protrusion 65T. You may. In this case, the rotation-regulating protrusion 65T and the receiving recess 20U engage with each other in a concavo-convex manner, so that the rotation of the double-cylinder component 65 is restricted and the cylinder penetrating portion 13B and the base penetrating portion 13A are prevented from being displaced. In addition, the generation of noise due to the rotation of the double cylinder component 65 can be prevented.

(5) In the first embodiment, the cylinder penetrating portion 13B has an oval shape, but the present invention is not limited to this, and it may be an elliptical shape, a rectangular shape, or a circular shape. A plurality of holes may be arranged in the vertical direction.

(6) In the first embodiment, the double cylinder component 65 and the upper support base 20A and the double cylinder component 65 and the lower support base 20B are sealed with separate O-rings 66R. However, for example, a groove 66M may be provided at a position corresponding to the boundary between the upper support base 20A and the lower support base 20B, or the upper cylinder receiving portion 25 of the upper support base 20A or the lower cylinder of the lower support base 20B may be provided. A notch may be provided at the opening edge of the receiving portion 26, and one O-ring 66R may be configured to seal between the two

support bases

20A and 20B. If the groove (notch) for the O-ring 66R is arranged not in the double cylinder part 65 but in the upper support base 20A or the lower support base 20B as in the latter, the resin double cylinder part 65 is formed. Since no parting line is generated, it is possible to seal more reliably.

(7) In the first embodiment, the O-ring seals between the double-cylinder component 65 and the upper and

lower support bases

20A and 20B, but a gasket may also be used. Further, the O-ring or the gasket may have a figure eight shape and may be configured to surround the double cylinder component 65 and the introduction path member 19A together.

(8) In the first embodiment, the first facing surface 13B1 of the cylinder penetrating portion 13B is arranged at a position deviated from the tangent line of the inner peripheral surface 12B of the gas-liquid separation chamber 12, but the gas-liquid separation chamber 12 It may be arranged on the tangent line of the inner peripheral surface 12B. Further, the first facing surface 13B1 may be inclined with respect to the tangent line of the inner peripheral surface 12B of the gas-liquid separation chamber 12, and the width of the first facing surface 13B1 and the second facing surface 13B2 becomes wider toward the inside. It may be inclined so as to be narrow.

(9) In the second embodiment, the number of communication holes 34 is one, but a plurality of communication holes 34 may be provided. Even in this case, it is preferable that the entire opening of the plurality of communication holes 34 is covered with the shutter portion 70A from above. The communication hole 34 may include a portion not covered by the shutter portion 70A.

(10) In the second embodiment, the leg portion 70C of the shutter member 70W is configured by bending the strip plate, but the strip plate may be overhanging in the horizontal direction. In this case, it is necessary to provide a contact portion for sandwiching the leg portion 70C in the second recess 20H of the lower support base 20B in cooperation with the lower end portion of the cylindrical portion 20G of the upper support base 20A. Further, the shutter member 70W may have a plurality of through holes at positions near the outer edge of the disk.

(11) In the second embodiment, the shutter member 70W may be provided with a rotation stopper. For example, as shown in FIG. 24, the shutter member 70W may be provided with a rotation stop leg 70K having an insertion hole 70S to be inserted into the regulation bar 72.

(12) As shown in FIG. 25, the configuration may include both the double cylinder component 65 of the first embodiment and the shutter member 70W of the second embodiment. In this case, a clearance is provided between the lower end of the double cylinder component 65 and the upper surface of the partition wall 39, and the shutter member 70W is sandwiched between them. As shown in the figure, the double cylinder component 65 may be positioned in the vertical direction by the legs 70C of the shutter member 70W, or a positioning flange or the like may be formed on the outer cylinder portion 66. It may be.

10,10W integrated valve 11 body 11A upper body 11B lower body 12 gas-liquid separation chamber 12A cylindrical body 12B inner peripheral surface 13 inflow port 13B cylinder penetration 20A upper support base 20B lower support base 34 communication hole 39 partition wall 65 Heavy cylinder parts 66 Outer cylinder part 67 Inner cylinder part 69

Inflow guide protrusion

70, 70W Shutter member

70A Shutter part

70C Leg part 80 Heat pump cycle

Claims

It is incorporated in a heat pump cycle having an indoor condenser, an outdoor evaporator, and a compressor, and the gas-liquid mixed refrigerant flowing from the indoor condenser is swirled along the inner peripheral surface of the gas-liquid separation chamber to separate and separate the gas and liquid. In the integrated valve that can be switched between the first state in which the liquid phase refrigerant is discharged to the outdoor evaporator and the second state in which the separated gas phase refrigerant is discharged to the compressor.
A gas-phase refrigerant outflow pipe arranged inside the gas-liquid separation chamber and allowing the separated gas-phase refrigerant to flow out of the gas-liquid separation chamber.
Between the gas-phase refrigerant outflow pipe and the outer cylinder portion which is tubular and whose inner peripheral surface forms the inner peripheral surface of the gas-liquid separation chamber, and between the gas-phase refrigerant outflow pipe and the outer cylinder portion. An integrated valve including a contact plate portion for communication and a double-cylinder component integrally molded with resin.
The double-cylinder parts are sandwiched in the axial direction, and the metal upper and lower support bases that line up vertically when the integrated valve is used, and the support bases on the upper and lower sides.
An outer cylinder through hole and a base through hole formed in the outer cylinder portion of the double cylinder component and the upper or lower support base, respectively, communicating with each other and taking in the gas-liquid mixing refrigerant into the gas-liquid separation chamber. When,
A first facing portion provided on the inner surface of the outer cylinder through hole and extending on the tangent line of the inner peripheral surface of the gas-liquid separation chamber or extending in parallel with the tangent line at a position near the tangent line.
The integrated valve according to claim 1, further comprising a second facing portion that is provided on the inner surface of the outer cylinder through hole and faces the first facing portion inside the first facing portion.
The cross-sectional shape of the outer cylinder through hole is elongated in the axial direction of the gas-liquid separation chamber, and the cross-sectional shape of the base through hole is a circle that exposes the entire outer cylinder through hole when viewed from the outside. The integrated valve according to claim 2.
According to claim 3, a plurality of straightening vanes are arranged in the outer cylinder through hole so as to communicate between the first facing portion and the second facing portion and arranged in the longitudinal direction of the outer cylinder through hole. The integrated valve described.
The integrated valve according to claim 4, wherein the straightening vane is inclined downward toward the gas-liquid separation chamber.
The integrated valve according to any one of claims 2 to 5, wherein the second facing portion has an inflow guide portion extending inward from a portion penetrating the cylinder wall of the outer cylinder portion.
The outer cylinder portion is provided so as to project inward from the inner peripheral surface of the gas-liquid separation chamber, and is curved from the inflow guide portion and the inner end portion of the inflow guide portion to the side opposite to the first facing portion. The integrated valve according to claim 6, further comprising an inflow guide protrusion having a curved surface that extends and contacts the inner peripheral surface of the gas-liquid separation chamber.
The integrated valve according to claim 7, wherein the inflow guide protrusion has a smaller amount of protrusion from the inner peripheral surface of the gas-liquid separation chamber as it goes downward.
The integrated valve according to claim 1, wherein the outer cylinder through hole is inclined downward as it goes inward.
The outer cylinder portion of the double cylinder component has a cylindrical shape.
Any one of claims 2 to 9 in which an engaging portion that engages with the double-cylinder component and the upper or lower support base in an uneven manner to regulate the rotation of the double-cylinder component is formed. The integrated valve according to the claim.