JP7157809B2 - integrated valve - Google Patents

Description

The present disclosure is incorporated in a heat pump cycle having an indoor condenser, an outdoor evaporator, and a compressor, and the gas-liquid mixture 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. and 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 gas-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 causes the separated gas-phase refrigerant to flow out from the gas-liquid separation chamber. is known (see, for example, Patent Literature 1).

JP 2013-92355 (paragraphs [0122] to [0123], FIG. 4)

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

The invention of claim 1, which has been made to solve the above problems, is incorporated in a heat pump cycle having an indoor condenser, an outdoor evaporator, and a compressor, and separates a gas-liquid mixed refrigerant flowing from the indoor condenser into a gas-liquid separation chamber. A first state in which gas-liquid separation is performed by swirling along the peripheral surface and the separated liquid-phase refrigerant flows out to the outdoor evaporator, and a second state in which the separated gas-phase refrigerant flows out to the compressor. and a gas-phase refrigerant outflow pipe that is arranged inside the gas-liquid separation chamber and causes the separated gas-phase refrigerant to flow out of the gas-liquid separation chamber, and the gas-phase refrigerant outflow pipe an outer cylindrical portion having a cylindrical shape and having an inner peripheral surface forming the inner peripheral surface of the gas-liquid separation chamber; and a connecting plate portion communicating between the gas-phase refrigerant outflow pipe and the outer cylindrical portion. are integrally molded of resin , upper and lower metal support bases sandwiching the double cylinder part in the axial direction and arranged vertically when the integrated valve is used, and the double cylinder part. an outer cylinder through-hole and a base through-hole formed in the outer cylinder part and the upper or lower support base, respectively, communicating with each other and introducing a gas-liquid mixed refrigerant into the gas-liquid separation chamber; a first opposing portion provided on the inner surface of the through hole and extending on a tangential line of the inner peripheral surface of the gas-liquid separation chamber or extending parallel to the tangential line at a position close to the tangential line; a second facing portion facing the first facing portion inside the first facing portion and having an inflow guide portion extending inward from a portion penetrating the cylindrical wall of the outer cylindrical portion; The inflow guide portion is provided in the outer cylindrical portion, protrudes inward from the inner peripheral surface of the gas-liquid separation chamber, and curves from the inner end portion of the inflow guide portion to the side opposite to the first facing portion. a curved surface that extends and communicates with the inner peripheral surface of the gas-liquid separation chamber; the inflow guide protrusion extends downward toward the inner peripheral surface of the gas-liquid separation chamber; It is an integrated valve with a small amount of protrusion from the surface .

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

FIG. 2 is a conceptual diagram of a heat pump cycle in which the integrated valve according to the first embodiment is incorporated; Front perspective view of integrated valve Rear view of integrated valve Front sectional view of the integrated valve Flat cross-sectional view near the shutter member Front sectional view of the integrated valve Perspective view of double tube member Front sectional view of double tube member Flat sectional view of the integrated valve Bottom perspective view of double tube member Front sectional view of the integrated valve according to the second embodiment Perspective view of shutter member Front view of shutter member Front sectional view near the shutter member The perspective view of the double cylinder member which concerns on a modification Front cross-sectional view of a double cylinder member according to a modification Bottom perspective view of a double cylinder member according to a modification Front cross-sectional view of a double cylinder member according to a modification AA sectional view in FIG. Front cross-sectional view of a double cylinder member according to a modification BB cross-sectional view in FIG. Bottom perspective view of a double cylinder member according to a modification Front sectional view of an integrated valve according to a modification Front cross-sectional view of the vicinity of the shutter member of the integrated valve according to the modification Front sectional view of an integrated valve according to a modification

[First embodiment]
The integrated valve 10 of this embodiment will be described below with reference to FIGS. 1 to 10. FIG. As shown in FIG. 1, the integrated valve 10 of the present embodiment is incorporated in, for example, a heat pump cycle 80 of an air conditioner of an electric vehicle or a hybrid vehicle that runs with the 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 (for example, inside the hood), and an indoor condenser 82 and an indoor evaporator 84 arranged inside the vehicle (inside the air conditioning unit). and can be switched between cooling mode and heating mode.

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

An indoor capacitor 82 is connected to the output port 81C of the compressor 81 . The indoor condenser 82 functions as a radiator that radiates heat (heats the vehicle interior) from the high-temperature, high-pressure refrigerant discharged from the output port 81C of the compressor 81 . In the cooling mode, the interior condenser 82 is covered with a cover, for example, so that the interior of the vehicle is not heated.

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, and functions as a radiator that dissipates heat from the refrigerant when the heat pump cycle 80 is in the cooling mode. Function.

A low-pressure input port 81A of the compressor 81 is connected to the output port of the outdoor heat exchanger 83 via an on-off valve 86 . 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-pressure 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 open, 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. 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 closed, the expansion valve 85 is opened, and refrigerant from the outdoor heat exchanger 83 flows into the indoor evaporator 84 . The indoor evaporator 84 absorbs heat from the air in the vehicle interior (cools the interior of the vehicle) and evaporates the refrigerant that has flowed in from the outdoor heat exchanger 83 .

As shown in FIG. 1, the integrated valve 10 has an inflow port 13 into which the refrigerant flows, a gas-liquid separation chamber 12 capable of separating the refrigerant flowing in from the inflow port 13, and the gas-liquid separation chamber 12. It has a gas-phase outflow port 14 for outflowing the gas-phase refrigerant and a liquid-phase outflow port 15 for outflowing 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 condenser 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 . In addition, the integrated valve 10 includes a drive valve 50 (a solenoid 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 separates the gas-liquid. A differential pressure valve 40 is provided between the chamber 12 and the gas phase outflow port 14, and by opening and closing the drive valve 50, the gas phase outflow port 14 can be opened and closed (specifically, the drive valve When the drive valve 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 details of the opening/closing control of the integrated valve 10 will be described later.

The heat pump cycle 80 has a normal heating mode and a special heating mode as heating modes. In the normal heating mode, the driven 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 passage 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. 1(B)). 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 outdoor temperature is extremely low, the outdoor evaporator (outdoor heat exchanger 83) cannot sufficiently absorb heat from the outdoor 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 rise and the flow rate of the refrigerant decreases. If the flow rate of the refrigerant decreases, the discharge pressure and temperature of the refrigerant from the compressor 81 will not increase, heat radiation from the indoor condenser 82 will decrease, and the heating capacity will decrease. On the other hand, in the special heating mode, the refrigerant before flowing into the outdoor heat exchanger 83 is gas-liquid separated by the gas injection cycle, and the separated gas-phase refrigerant is returned to the compressor 81 . As a result, the refrigerant before the pressure is lowered in the outdoor heat exchanger 83 is added to the compressor 81, so that the pressure drop of the refrigerant discharged from the compressor 81 can be suppressed. As a result, it becomes possible to improve the heating performance.

Next, details of the integrated valve 10 will be described. As shown in FIGS. 2 to 4, the integrated valve 10 has a plurality of flow paths inside a vertically elongated body 11 . The integrated valve 10 is arranged such that the longitudinal direction of the body 11 is the vertical direction during use (that is, when the integrated valve 10 is installed in a vehicle). In the following description, the up-down direction of the integrated valve 10 when the integrated valve 10 is in use is defined as the up-down direction of the integrated valve 10 . Further, the horizontal direction in FIG. 4 is the horizontal 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 vertically connecting an upper body 11A and a lower body 11B. The upper body 11A has a block-shaped upper support base 20A which is made of metal and is square in front view, and the lower body 11B has a lower support base 20B which is made of metal and has a substantially rectangular parallelepiped shape. 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 vertically, and a cylindrical body 12A hangs down from the ceiling coaxially with the central axis. An inflow port 13 that communicates the outside of the integrated valve 10 with the gas-liquid separation chamber 12 is opened at the rear upper right portion 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 gas-liquid mixed refrigerant 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, Due to the centrifugal force caused by this swirling, the refrigerant is separated into a vapor phase refrigerant and a liquid phase refrigerant. The separated gas-phase refrigerant flows upward through the inside of the cylindrical body 12A, and the separated liquid-phase refrigerant falls downward along the inner peripheral surface 12B of the gas-liquid separation chamber 12. FIG.

A first straight hole portion 21 and a second straight hole portion 31 extending parallel to 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 of the lower support base 20B of the lower body 11B to a position near the left surface. The first straight hole portion 21 has a reduced diameter portion 21A whose diameter is reduced in a stepped manner toward the left from the right end opening, and a diameter that is tapered from the end of the reduced diameter portion 21A and has a uniform diameter. It has an inflow portion 21B that extends leftward 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 portion 21 with a uniform diameter. .

A support body 53 for the driven valve 50 that directly moves in the first straight hole 21 is attached to the right surface of the lower support base 20B, and the right end opening of the first straight hole 21 is closed by the support body 53. ing. The support body 53 is positioned by receiving a portion thereof in the diameter-reduced portion 21A of the first straight hole portion 21 . A space between the support body 53 and the reduced diameter portion 21A of the first straight hole portion 21 is sealed by an O-ring 53R. The driven valve 50 opens and closes a later-described valve port 62 by means of a valve element 51 provided at its tip. The driven valve 50 is in an open state away from the valve port 62 in a non-operating state, and is in a closed state by being placed against the opening edge of the valve port 62 (that is, the valve seat 62Z) in an operating state.

A cylindrical heat insulating member 60 made of a material (for example, resin) having a lower thermal conductivity than the upper and lower support bases 20A and 20B is fitted in the left portion of the first straight hole portion 21. . The space between the lower support base 20B and the heat insulating member 60 is sealed by an O-ring 60R arranged in the middle of the heat insulating member 60 in the axial direction. A right end portion of the heat insulating member 60 is arranged in the inflow portion 21B with a gap from the inner surface of the inflow portion 21B. A right end opening of the heat insulating member 60 constitutes a valve port 62 that is opened and closed by the driven valve 50 . The insides of the first straight hole portion 21 and the heat insulating member 60 form a liquid-phase refrigerant flow path 21R.

The liquid-phase outflow port 15 described above is formed through 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). . The heat insulating member 60 is configured such that an engaging projection 64 provided on a part of the left end face in the circumferential direction is engaged with an engaging recess 24 formed at the left end of the first straight hole 21 to form an uneven surface. , is locked against the body 11 . In addition, by engaging a restricting bar 72 attached to a partition wall 39, which will be described later, with an engagement recess 63 formed on the outer peripheral surface of the heat insulating member 60, rightward movement of the heat insulating member 60 is restricted. there is

An orifice 61 is formed at the lower right end of the heat insulating member 60 to extend in the radial direction and communicate the inside of the heat insulating member 60 with the inflow portion 21B of the first straight hole portion 21 . 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 that partitions the gas-liquid separation chamber 12 and the first straight hole 21. As shown in FIG. A communicating hole 34 extending vertically and communicating between 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 that is arranged directly below the gas-liquid separation chamber 12 . A lower end portion of the communication hole 34 opens to the inflow portion 21B. The communication holes 34 are formed at two positions facing each other across the center of the outer edge of the partition wall 39 (see FIG. 5).

As shown in FIGS. 4 and 5, the upper surface of the partition wall 39 has a protrusion 39T that protrudes upward at the center. A 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 suspended from the center of the lower surface of a disk-shaped shutter portion 70A. The insertion bar 70B is press-fitted into the first engaging hole 39A. The shutter portion 70A covers a portion 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 penetrating through the partition wall 39 at a position offset from the first engagement hole 39A in the horizontal direction and covered from above by the shutter portion 70A. The restriction bar 72 described above is attached to the second 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 near the right surface. Behind the right end portion of the upper support base 20A, the gas phase outflow port 14 is formed penetrating from the rear surface of the upper support base 20A to the second straight hole portion 31. The gas phase outflow port 14 is , the outside of the integrated valve 10 and the right end of the second straight hole portion 31 are communicated. A middle portion of the second straight hole portion 31 is communicated with an inner portion of the cylindrical body 12A of the gas-liquid separation chamber 12 by a communication hole 32 . A portion of the second straight hole portion 31 close to the gas phase outflow port 14 has a stepped diameter reduction from the left side thereof, and an annular concave portion 31U is formed in the stepped portion 31D therebetween. It is

A differential pressure valve 40 capable of opening and closing a 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 of the second straight hole portion 31 is closed by a 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 biased toward the stepped portion 31D by a compression coil spring 42, and the valve body 41 provided in the differential pressure valve 40 normally closes the valve port 43 on the inner edge of the stepped portion 31D from the left side. there is A gap is provided between the differential pressure valve 40 and the recessed portion 31U of the stepped portion 31D. is configured to Thereby, the differential pressure valve 40 can receive the pressure inside the communication hole 32 (that is, the pressure inside 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 by the internal pressure introduction path 19. As shown in FIG. An introduction path member 19A for sealing between the upper support base 20A and the lower support base 20B is disposed in the middle of the internal pressure introduction path 19, and the introduction path member 19A and the upper and lower sides and the support bases 20A and 20B are sealed by O-rings 19R.

In the integrated valve 10 of this 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 opening 62 is opened, as shown in FIG. In this case, the pressure in the recess 31U through the communication hole 32 is higher than the pressure of the refrigerant in the first straight hole 21 (inside the heat insulating member 60) through the internal pressure introduction passage 19 (back pressure of the valve element 41). is not strong enough to move the valve body 41 to the valve open position, and the valve body 41 biased by the compression coil spring 42 is maintained so that the valve port 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 closed, and the liquid refrigerant flows out only from the liquid phase outflow port 15 .

When the heat pump cycle 80 switches to the special heating mode, the driven 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. , flows through the orifice 61 into the inner portion of the insulating member 60 without passing through the valve opening 62 . At this time, the refrigerant in the liquid phase is decompressed by flowing into the large-diameter heat insulating member 60 from the small-diameter orifice 61 . The back pressure of the valve body 41 of the differential pressure valve 40 becomes equal to the pressure inside the first straight hole portion 21 by the internal pressure introduction passage 19 . When the pressure in the communication hole 32 becomes higher than the back pressure of the valve body 41, the valve body 41 opens the valve port 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 strictly parallel state but also a substantially parallel state (for example, a state of being inclined with respect to each other at an angle of 5 degrees or less).

Now, in the integrated valve 10 of the present embodiment, as shown in FIG. 4, the upper body 11A is formed by assembling the above-described upper support base 20A with a double cylinder part 65 having the gas-liquid separation chamber 12 inside. . Specifically, the upper support base 20A is formed with an upper tube receiving portion 25 recessed upward from the bottom surface, while the lower support base 20B is formed with a lower tube receiving portion recessed downward from the upper surface. A portion 26 is formed. Both the upper tube receiving portion 25 and the lower tube receiving portion 26 have the same circular cross-sectional shape, and the inner peripheral surfaces of the upper tube receiving portion 25 and the lower tube receiving portion 26 are flush with each other. A communication hole 32 is opened in the ceiling surface of the upper tube receiving portion 25 . The lower end portion of the communication hole 32 forms an enlarged diameter portion 32A that is stepped and has a larger diameter than the upper portion thereof. Further, the upper surface of the partition wall 39 described above constitutes the bottom surface of the lower tube receiving portion 26 .

A double tube component 65 shown in FIG. 7 is fitted inside the upper tube receiving portion 25 and the lower tube receiving portion 26 . The double cylinder part 65 is an integrally foamed product made of resin (for example, PPS), and has 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 tube component 65 includes an outer tube portion 66 that abuts against the inner peripheral surfaces of the upper tube receiving portion 25 and the lower tube receiving portion 26, and an inner side of the outer tube portion 66. and an annular plate portion 68 connecting between 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. The inner diameter of the upper portion of the tapered portion 66A is larger than that of the tapered portion 66A. In addition, two grooves 66M in which two O-rings 66R are mounted to respectively seal between the upper support base 20A and the lower support base 20B are formed in the outer peripheral surface of the outer cylindrical portion 66. As shown in FIG.

The inner tubular portion 67 extends from a position above the upper end of the outer tubular portion 66 to a position above the lower end of the outer tubular portion 66 by about ⅓ of the length in the axial direction of the outer tubular portion 66 . faces the shutter portion 70A from above. When viewed from below, the entire lower end opening of the inner cylindrical portion 67 is covered with 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 abuts the ceiling surface of the upper cylinder receiving portion 25 . A portion of the inner cylinder portion 67 above the annular plate portion 68 is received in the enlarged diameter portion 32A of the communication hole 32 of the upper cylinder receiving portion 25 . A portion of the inner cylindrical portion 67 below the annular plate portion 68 forms the cylindrical body 12A described above.

As shown in FIGS. 3 and 9, in the integrated valve 10 of the present embodiment, the inflow port 13 is formed in the base through portion 13A formed through the upper support base 20A and the outer cylinder portion 66 of the double cylinder component 65. and a cylinder through portion 13B provided. The base penetrating portion 13A of the upper support base 20A has a circular cross section, and its opening edge is tapered outwardly. In addition, FIG. 9 is the figure which looked at the plane cross section of the integrated valve 10 from the downward direction. In addition, in the present disclosure, the term “circular” includes not only a perfect circle but also a shape slightly distorted from a perfect circle.

Next, the cylinder penetration portion 13B of the double cylinder component 65 will be described in detail. As shown in FIG. 10, an inflow guide projection 69 projecting inward from the inner peripheral surface of the outer cylinder portion 66 is integrally formed on the upper portion of the outer cylinder portion 66. The inflow guide projection 69 and the outer cylinder are integrally formed. A cylindrical through portion 13B is provided to pass through 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. Among the surfaces, a first surface 69A extending leftward from a position slightly to the left rear of the rightmost portion, and from the left end of the first surface 69A, extending while curving to the left rearward, the inner circumference of the outer cylindrical portion 66 and a third surface 69C connecting the lower ends of the first surface 69A and the second surface 69B and the inner peripheral surface of the outer cylindrical portion 66. As shown in FIG. The second surface 69B extends from the vicinity of the rear end portion of the inner peripheral surface of the outer cylindrical portion 66 to the left end of the first surface 69A while increasing its curvature. Between the first surface 69A and the inner cylindrical portion 67, there is provided a gap of approximately the same length as the lateral width of the first surface 69A.

As shown in FIG. 9 , the cylinder through 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 penetration portion 13B is an elliptical shape, and the cylinder penetration portion 13B has a first facing surface 13B1 and a second facing surface 13B1 facing each other in the width direction (horizontal direction). It has a facing surface 13B2. As shown in FIG. 9, in the cross section of the integrated valve 10, the first opposing surface 13B1 is slightly to the left of an imaginary tangent line L (a tangent line extending in the front-rear direction) passing through the rightmost end of the inner circumference of the outer cylindrical portion 66. , and extends parallel to the imaginary tangent line L from a position near the right end of the first surface 69A. The second opposing surface 13B2 extends parallel to the first opposing surface 13B1 from a position near the left end of the first surface 69A. A portion of the second opposing surface 13B2 that protrudes inward from the inner peripheral surface of the outer cylindrical 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 elliptical shape. Further, as shown in FIG. 3, the entire opening edge of the cylinder through portion 13B is exposed by the base through portion 13A when viewed from the outside.

The structure of the integrated valve 10 of this embodiment is as described above. Next, the effect of the integrated valve 10 is demonstrated. According to the integrated valve 10 of the present embodiment, the outer cylindrical portion 66 having the inner peripheral surface 12B of the gas-liquid separation chamber 12 and the cylindrical body 12A through which the gas-phase refrigerant passes are molded of resin. When the refrigerant swirls on the inner peripheral surface 12B of the gas-liquid separation chamber 12, when the liquid-phase refrigerant travels along the inner peripheral surface 12B of the gas-liquid separation chamber 12, and when the gas-phase refrigerant passes through the cylindrical body 12A In addition, the heat is less likely to be transmitted to the outside through the upper support base 20A and the lower support base 20B, thereby improving thermal efficiency. In particular, when the upper support base 20A and the lower support base 20B are made of metal as in this embodiment, the effect is more pronounced.

Further, the first opposing surface 13B1 of the cylindrical through 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 in the vicinity of the tangential line of the inner peripheral surface 12B of the gas-liquid separation chamber 12. In addition, since it extends parallel to the tangent line, the inflowing refrigerant can be easily made to follow the inner peripheral surface 12B of the gas-liquid separation chamber 12 . In addition, since the cylindrical through portion 13B has an elliptical cross-sectional shape, the width in the radial direction is reduced, making it easier for a larger amount of refrigerant to flow along the inner peripheral surface 12B of the gas-liquid separation chamber 12. flow rate can be secured. Further, by configuring the inflow port 13 from the cylindrical through portion 13B and the base through portion 13A, the hole (base through portion 13A) formed in the metal upper support base 20A can be circular in cross section, The generation of burrs can be prevented more than when the cross section is oval.

Further, in the integrated valve 10 of the present embodiment, the cylinder penetration portion 13B of the outer cylinder portion 66 is provided with the inflow guide portion 69R projecting inward from the inner peripheral surface 12B of the gas-liquid separation chamber 12. This makes it easier for the refrigerant that has flowed in from the portion 13B to follow the inner peripheral surface 12B of the gas-liquid separation chamber 12 . In addition, since the second surface 69B of the inflow guide protrusion 69 is curved, the swirl of the refrigerant is more pronounced than in 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. Hard to get in the way. It should be noted that the liquid-phase refrigerant is generally caught on the inner peripheral surface during the time when the gas-liquid mixed refrigerant flows in from the inflow port 13 and makes one turn (the amount of protrusion of the inflow guide projection and the length in the vertical direction etc.).

[Second embodiment]
The integrated valve 10W of 2nd Embodiment is shown by FIGS. 11-14. As shown in FIG. 10, the integrated valve 10W of this embodiment differs from the integrated valve 10 of the first embodiment in the configuration around the shutter member. In the following, parts having the same configurations as those of the first embodiment are denoted by the same reference numerals, description thereof is omitted, and only different points are described.

As shown in FIG. 12, the shutter members 70W of the present embodiment are arranged radially (at positions dividing the outer periphery of the shutter portion 70A into three equal parts) on the disk-shaped shutter portion 70A and the outer edge portion of the shutter portion 70A. and three legs 70C. As shown in FIG. 13, the leg portion 70C has a band-like shape, and includes a first band portion 70D extending downward while facing outward from the outer edge of the shutter portion 70A, and a U-shaped portion extending from the end portion of the first band portion 70D. A second belt portion 70E that is folded back in a letter shape and extends upward while facing outward, and a position that is one or two plate thicknesses below the shutter portion 70A and is bent horizontally outward from the second belt portion 70E. , and a horizontally extending third belt portion 70F.

As shown in FIG. 11, the shutter member 70W is sandwiched between the upper body 11A and the lower body 11B. 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 bottom surface of the upper support base 20A of the upper body 11A, and a first A cylindrical portion 20G projecting downward from the opening edge of the recess 20F is formed, while a second recess 20H recessed downward from the upper surface is formed in 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 concave portion 20H of the lower support base 20B, the gas-liquid separation chamber 12 is formed inside.

There is a gap between the lower end of the cylindrical portion 20G and the bottom surface of the second recess 20H of the lower support base 20B (upper surface of the partition wall 39), 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 portion 70G between the first band portion 70D and the second band portion 70E of the leg portion 70C abuts the bottom surface of the second concave portion 20H of the lower support base 20B. The shutter member 70W is prevented from coming off in the vertical direction by the contact of the third belt portion 70F with the lower end of the cylindrical portion 20G. Further, since the leg portion 70C is formed by bending a band plate, the shutter portion 70A is elastically deformed in the horizontal direction, and horizontal movement and rotation 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 this embodiment, one communication hole 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 this embodiment is made of resin, aluminum, or the like, and is crimped and fixed to the upper support base 20A.

The configuration of the integrated valve 10W of the present embodiment is as described above. Next, the effects of the integrated valve 10W will be described. According to the integrated valve 10W of the present embodiment, since the shutter member 70W is sandwiched between the upper body 11A and the lower body 11B, it is possible to increase the dimensional tolerance compared to the conventional method in which the shutter member is press-fitted. can be made, making processing easier. In addition, after the shutter member 70W is placed in the second concave portion 20H of the lower support base 20B, the shutter member 70W can be assembled by attaching the upper support base 20A from above, so that the shutter member 70W can be easily assembled. become. Furthermore, 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. (Particularly, the lower end of the cylindrical body 12A) can be made less likely to get dirty.

[Other embodiments]
(1) In the above-described first embodiment, as shown in FIGS. 15 to 17, a plurality of rectifying plates 13B3 arranged in the longitudinal direction may be provided inside the cylindrical through portion 13B.

(2) Further, as shown in FIGS. 18 and 19, the current plate 13B3 may be configured to be inclined downward toward the inside. In this case, the refrigerant can be smoothly guided downward while swirling. In the example shown in FIGS. 18 and 19, the cylinder penetration portion 13B itself is also inclined, and the refrigerant can be guided downward more smoothly. Note that the cylinder penetrating portion 13B may extend horizontally.

(3) Further, as shown in FIGS. 20 to 22, the projection amount of the inflow guide protrusion 69 may decrease downward. In this case, the inflow guide protrusion 69 can prevent the refrigerant that flows in from the cylinder penetration portion 13B and swirls from leaving the inner peripheral surface 12B of the gas-liquid separation chamber 12 and moving inward.

(4) In the above-described first embodiment, as shown in FIG. 23, the double cylindrical part 65 is provided with the rotation restricting protrusion 65T, and the upper support base 20A is provided with the receiving recess 20U for receiving the rotation restricting protrusion 65T. may In this case, the rotation restricting protrusion 65T and the receiving recess 20U are engaged with each other to restrict the rotation of the double tube component 65, thereby preventing the tube penetrating portion 13B and the base penetrating portion 13A from being displaced. Also, the generation of noise due to the rotation of the double cylinder part 65 is prevented.

(5) In the above-described first embodiment, the cylindrical through portion 13B has an elliptical shape. A plurality of holes may be arranged in the vertical direction.

(6) In the first embodiment, separate O-rings 66R are used to seal between the double cylindrical component 65 and the upper support base 20A and between the double cylindrical component 65 and the lower support base 20B. However, for example, a groove 66M may be provided at a position corresponding to the boundary portion between the upper support base 20A and the lower support base 20B, or the upper tube receiving portion 25 of the upper support base 20A or the lower tube of the lower support base 20B may be provided. A notch may be provided in the opening edge of the receiving portion 26, and a single O-ring 66R may be used to seal between the support bases 20A and 20B. As in the latter case, if the groove (notch) for the O-ring 66R is arranged in the upper support base 20A or the lower support base 20B instead of the double cylinder part 65, the double cylinder part 65 made of resin can be formed. Since there is no parting line, more reliable sealing is possible.

(7) In the first embodiment, the O-ring seals between the double cylindrical part 65 and the upper and lower support bases 20A and 20B, but a gasket may be used. Alternatively, the O-ring or gasket may be shaped like a figure 8 to surround both the double cylindrical member 65 and the introduction path member 19A.

(8) In the first embodiment, the first facing surface 13B1 of the cylindrical through portion 13B is arranged at a position deviated from the tangential line of the inner peripheral surface 12B of the gas-liquid separation chamber 12. It may be arranged on the tangential line of the inner peripheral surface 12B. Moreover, the first opposing 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 opposing surface 13B1 and the second opposing surface 13B2 may decrease as it goes inward. You may incline so that it may become narrow.

(9) Although there is one communication hole 34 in the second embodiment, a plurality of communication holes may be provided. Even in this case, it is preferable that the entire openings of the plurality of communication holes 34 are covered with the shutter portion 70A from above. In addition, the communication hole 34 may include a portion not covered with the shutter portion 70A.

(10) In the above-described second embodiment, the leg portion 70C of the shutter member 70W is formed by bending the band plate, but the band plate may be projected in the horizontal direction. In this case, the second recess 20H of the lower support base 20B needs to be provided with an abutting portion that cooperates with the lower end of the cylindrical portion 20G of the upper support base 20A to clamp the leg portion 70C. Further, the shutter member 70W may be configured to have a plurality of through holes at positions near the outer edge of the disk.

(11) In the above 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 stopping leg portion 70K having an insertion hole 70S through which the regulation bar 72 is inserted.

(12) As shown in FIG. 25, it may be configured to have 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 part 65 and the upper surface of the partition wall 39, and the shutter member 70W is sandwiched therebetween. As shown in the figure, the double cylinder part 65 may be configured to be vertically positioned by the leg portion 70C of the shutter member 70W, or may be configured to form a positioning flange or the like on the outer cylinder portion 66. 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 Two Double cylinder part 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 (6)

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 the gas and liquid, and the separation is performed. a first state in which the separated liquid-phase refrigerant flows out to the outdoor evaporator, and a second state in which the separated gas-phase refrigerant flows out to the compressor,
a gas-phase refrigerant outflow pipe disposed inside the gas-liquid separation chamber for causing the separated gas-phase refrigerant to flow out from the gas-liquid separation chamber;
the gas-phase refrigerant outflow pipe, a cylindrical outer cylindrical portion having an inner peripheral surface forming the inner peripheral surface of the gas-liquid separation chamber, and a space between the gas-phase refrigerant outflow pipe and the outer cylindrical portion A double cylinder part in which a communicating plate portion that communicates with a resin is integrally molded ,
upper and lower support bases made of metal that sandwich the double cylinder part in the axial direction and are vertically aligned when the integrated valve is in use;
An outer cylinder through-hole and a base through-hole formed in the outer cylinder portion of the double cylinder part and the upper or lower support base, respectively, communicate with each other, and introduce the gas-liquid mixed refrigerant into the gas-liquid separation chamber. When,
a first opposing portion provided on the inner surface of the outer cylinder through-hole and extending on a tangential line of the inner peripheral surface of the gas-liquid separation chamber or extending parallel to the tangential line at a position near the tangential line;
An inflow guide portion provided on the inner surface of the outer cylinder through-hole, opposed to the first opposed portion on the inner side of the first opposed portion, and extending inward from a portion penetrating the cylinder wall of the outer cylinder portion. a second facing portion having
The inflow guide portion is provided in the outer cylindrical portion, protrudes inward from the inner peripheral surface of the gas-liquid separation chamber, and curves from the inner end portion of the inflow guide portion to the side opposite to the first opposing portion. an inflow guide protrusion having a curved surface that extends along the length of the gas-liquid separation chamber and communicates with the inner peripheral surface of the gas-liquid separation chamber;
The integrated valve , wherein the amount of protrusion of the inflow guide protrusion from the inner peripheral surface of the gas-liquid separation chamber decreases toward the bottom . 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 circular shape that exposes the entire outer cylinder through-hole when viewed from the outside. The integrated valve according to claim 1. 3. A plurality of flow straightening vanes arranged in the longitudinal direction of the outer cylinder through-hole are arranged in the outer cylinder through-hole so as to communicate between the first opposing portion and the second opposing portion. Integrated valve as described. 4. The integrated valve according to claim 3, wherein said rectifying plate is inclined downward toward said gas-liquid separation chamber. The integrated valve according to any one of claims 1 to 4, wherein the outer cylinder through-hole is inclined downward toward the inner side. The outer cylinder portion of the double cylinder component has a cylindrical shape,
6. Any one of claims 1 to 5, wherein an engaging portion is formed in said double tubular component and said upper or lower support base to engage with projections and recesses to restrict rotation of said double tubular component. The integrated valve according to claim 1.

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