JP6947401B2 - Flow switching valve - Google Patents

Description

The present invention relates to a flow path switching valve that switches the flow path by moving the valve body, and relates to a flow path switching valve suitable for switching the flow path in, for example, a heat pump type air-conditioning system.

Generally, in a heat pump type air-conditioning system such as a room air conditioner, in addition to a compressor, an outdoor heat exchanger, an indoor heat exchanger, an expansion valve, etc., a flow path switching valve (four-way switching) as a flow path (flow direction) switching means is used. A valve or a six-way switching valve) is provided, and the operation mode (cooling operation and heating operation) is switched by the flow path switching valve.

As a flow path switching valve incorporated in a heat pump type heating / cooling system or the like as described above, one in which one sliding main valve body is slidably arranged in a valve body (main valve housing) is well known. However (see, for example, Patent Document 1 and the like), instead, as described in Patent Document 2, for example, a system in which a plurality of sliding valve bodies are integrally used has already been proposed.

There are three sliding flow path switching valves (six-way switching valves) on the opposite side of the axis of the tubular main valve housing that defines the main valve chamber and the axis of the main valve housing (main valve chamber). A total of 6 ports) are arranged in the main valve seat having a valve seat surface with an open surface, and in the main valve chamber so as to be movable in the axial direction, and are slidably contacted with the valve seat surface. A first U-turn passage (high-pressure side U-turn passage) having a slidable main valve body, and the main valve body having two ports out of the three ports selectively communicate with each other. A second slide valve body having a second U-turn passage (low-pressure side U-turn passage) for selectively communicating one slide valve body (high-pressure side slide valve body) and two of the other three ports. (Low pressure side slide valve body), and these slide valve bodies are arranged back to back so that the respective U-turn passages open in opposite directions, and the slide valve bodies are integrated in the axial direction. A port that is movable and slidable to each other in a direction perpendicular to the axis, and is communicated via the U-turn passage by moving the main valve body in the main valve chamber. The space (flow path) can be switched.

Further, in the slide type flow path switching valve (six-way switching valve) described above, a fluid having a relatively high pressure in the first U-turn passage (high-pressure side U-turn passage) of the first slide valve body (high-pressure side slide valve body). Is introduced, a relatively low-pressure fluid is introduced into the second U-turn passage (low-pressure side U-turn passage) of the second slide valve body (low-pressure side slide valve body), and the high-pressure side slide valve body and the low-pressure side slide are introduced. A pressure chamber into which a part of the high-pressure fluid introduced into the high-pressure side U-turn passage is introduced is provided between the valve body and the pressure chamber in the high-pressure side slide valve body when viewed in a direction perpendicular to the axis. The pressure receiving area on the side (back pressure side) is made larger than the pressure receiving area on the main valve seat side provided with the three ports, that is, the opening area of the high pressure side U-turn passage of the high pressure side slide valve body.

Therefore, when a high-pressure refrigerant is introduced into the high-pressure side U-turn passage and a part of the high-pressure refrigerant introduced into the high-pressure side U-turn passage is filled in the pressure chamber, the pressure and high pressure received from the pressure chamber (high-pressure refrigerant). Due to the pressure difference from the pressure received from the refrigerant (high pressure refrigerant) flowing through the side U-turn passage, the annular sealing surface of the high pressure side slide valve body is pressed against the valve seat surface of the main valve seat, making it difficult for the valve to leak.

Japanese Unexamined Patent Publication No. 8-170864 Japanese Unexamined Patent Publication No. 2018-0446666

However, in the conventional flow path switching valve described in Patent Document 2 and the like, as described above, the pressure chamber side of the high pressure side slide valve body is larger than the opening area of the high pressure side U-turn passage of the high pressure side slide valve body. The pressure receiving area on the (back pressure side) is set to be larger (wider), but on the high pressure side slide valve body than on the contact surface (annular seal surface) of the high pressure side slide valve body with the valve seat surface of the main valve seat. Since the pressure receiving area on the pressure chamber side (back pressure side) is set smaller, the pressure (surface pressure) distribution on the contact surface (annular sealing surface) of the high pressure side slide valve body becomes non-uniform, and the sealing performance and operability , Stability may decrease.

The present invention has been made in view of the above circumstances, and an object of the present invention is to provide a flow path switching valve capable of ensuring good sealing performance, operability, and stability, and effectively suppressing valve leakage. To provide.

In order to achieve the above object, the flow path switching valve according to the present invention is basically arranged in the main valve housing defining the main valve chamber and the main valve chamber, and a plurality of ports are opened. A first main valve seat having a valve seat surface and a plurality of ports are arranged in the main valve chamber on the opposite side of the first main valve seat with respect to the axis of the main valve chamber, and a plurality of ports are opened. A high-pressure side slide valve that has a second main valve seat having a valve seat surface and a high-pressure side U-turn passage into which a relatively high-pressure fluid is introduced and is slidable on the valve seat surface of the first main valve seat. A pair of slide valve bodies of a low pressure side slide valve body which has a body and a low pressure side U-turn passage into which a relatively low pressure fluid is introduced and is slidable on the valve seat surface of the second main valve seat. The main valve body is configured to have and is arranged in the main valve chamber so as to be movable in the axial direction, and the pair of slide valve bodies are integrally movable in the axial direction and are movable in the axial direction. It is slidable with each other in a direction perpendicular to the axis, and by moving the main valve body in the main valve chamber, each of the first main valve seat and the second main valve seat is provided. A flow path switching valve in which communication between the plurality of ports is switched, and the pair of slide valve bodies is formed around the opening of the high pressure side U-turn passage in the high pressure side slide valve body. An annular seal surface facing the seat surface is formed, and the outer shape of the pressure receiving surface on the low pressure side slide valve body side of the high pressure side slide valve body is the outer shape of the annular seal surface when viewed in a direction perpendicular to the axis. The feature is that it is set larger than the outer shape.

In a preferred embodiment, the annular sealing surface is formed only in a predetermined width around the opening of the high pressure side U-turn passage.

In another preferred embodiment, a convex surface portion having the same height as the annular seal surface and narrower than the annular seal surface is continuously provided at the axial end portion of the annular seal surface.

In a more preferred embodiment, the convex surface portion is provided so as to be located inside the pressure receiving surface on the low pressure side slide valve body side when viewed in a direction perpendicular to the axis line.

In a more preferred embodiment, when viewed in a direction perpendicular to the axis, the root portion of the convex surface portion is located inside the pressure receiving surface on the low pressure side slide valve body side, and the tip portion of the convex surface portion is the said. It is provided so as to be located outside the pressure receiving surface on the low pressure side slide valve body side.

In a more preferred embodiment, the convex surface portion is provided at least at the central portion in the width direction of the annular sealing surface.

In another preferred embodiment, an annular seal member is disposed between the high pressure side slide valve body and the low pressure side slide valve body, and the outer shape of the seal member is set to be larger than the outer shape of the annular seal surface. ..

In another preferred embodiment, the high pressure side slide valve body has a tubular shape, and a fitting convex portion slidably fitted in one side surface of the low pressure side slide valve body. Is provided, and the fitting convex portion is internally fitted into the high pressure side slide valve body, so that the inner peripheral surface of the high pressure side slide valve body and the end surface of the fitting convex portion provide the high pressure side U-turn passage. Is defined, and the high-pressure side slide valve body and the low-pressure side slide valve body are integrally movable in the axial direction and slidable with each other in a direction perpendicular to the axis. At the same time, the low pressure side U-turn passage is opened on the other side surface of the low pressure side slide valve body.

In the flow path switching valve according to the present invention, the outer shape of the pressure receiving surface on the low pressure side slide valve body side (back pressure side) of the high pressure side slide valve body is an annular seal on the high pressure side slide valve body when viewed in a direction perpendicular to the axis. Since it is set larger than the outer shape of the surface, the pressure distribution on the contact surface (annular seal surface) of the high-pressure side slide valve body with the valve seat surface of the main valve seat is substantially smaller than that of the conventional flow path switching valve described above. Since it becomes uniform, good sealing performance, operability, and stability can be ensured, and valve leakage can be effectively suppressed.

Issues, configurations, and effects other than those described above will be clarified by the following embodiments.

The vertical sectional view which shows the 1st communication state (during the cooling operation) of the 1st Embodiment of the flow path switching valve which concerns on this invention. The vertical sectional view which shows the 2nd communication state (during heating operation) of 1st Embodiment of the flow path switching valve which concerns on this invention. An enlarged vertical cross-sectional view of a main part of the flow path switching valve shown in FIG. 1 in an enlarged manner. FIG. 3 is a cross-sectional view taken along the line of sight of the VV arrow in FIG. FIG. 3 is a cross-sectional view taken along the line of sight of the arrow W of FIG. FIG. 5 is a cross-sectional view taken along the line of sight of the UU arrow in FIG. The perspective view which shows the main valve body and the coupling body of 1st Embodiment of the flow path switching valve which concerns on this invention. It is an enlarged view which shows the four-way pilot valve used for the flow path switching valve which concerns on this invention. A vertical cross-sectional view showing each state (during heating operation) (when energization is ON). An enlarged vertical cross-sectional view of a main part of another example of the flow path switching valve shown in FIG. 1 in an enlarged manner. FIG. 9 is a cross-sectional view taken along the line of sight of the VV arrow in FIG. FIG. 9 is a cross-sectional view taken along the line of sight of the arrow W of FIG. An enlarged vertical sectional view of a main part of the second embodiment of the flow path switching valve according to the present invention. FIG. 12 is a cross-sectional view taken along the line of sight of the VV arrow in FIG. FIG. 12 is a cross-sectional view taken along the line of sight of the arrow W of FIG. The perspective view which shows the main valve body and the coupling body of the 2nd Embodiment of the flow path switching valve which concerns on this invention. An enlarged vertical sectional view of a main part of a third embodiment of the flow path switching valve according to the present invention. FIG. 16 is a cross-sectional view taken along the line of sight of the VV arrow in FIG. FIG. 16 is a cross-sectional view taken along the line of sight of the arrow W of FIG. The perspective view which shows the main valve body and the coupling body of the 3rd Embodiment of the flow path switching valve which concerns on this invention. FIG. 6 is a cross-sectional view of the fourth embodiment of the flow path switching valve according to the present invention, which is shown according to the WW arrow line of sight of FIG.

Hereinafter, embodiments of the present invention will be described with reference to the drawings.

(First Embodiment)
1 and 2 are vertical cross-sectional views showing a first embodiment of a flow path switching valve (six-way switching valve) according to the present invention, FIG. 1 is a first communication state (during cooling operation), and FIG. , 2 is a diagram showing a second communication state (during heating operation).

In this specification, the descriptions indicating the positions and directions such as up / down, left / right, front / back, etc. are added for convenience according to the drawings in order to avoid complicated explanations, and are actually incorporated into a heat pump type air-conditioning system or the like. It does not always point to the position or direction in the state of being in the air conditioner.

Further, in each drawing, the gap formed between the members, the separation distance between the members, etc. are larger than the dimensions of each constituent member in order to facilitate understanding of the invention and for convenience in drawing. Or it may be drawn small.

The flow path switching valve 1 of the illustrated embodiment is, for example, a slide type used as a six-way switching valve in a heat pump type air-conditioning system, and is basically a cylinder type six-way valve main body 10 and a single electromagnetic wave as a pilot valve. It is equipped with a four-way pilot valve 90. The six ports provided in the flow path switching valve 1 of the present embodiment have the same reference numerals corresponding to the ports pA to pF of the six-way switching valve described in Patent Documents 1 and 2. Has been done. For the basic configuration of the heat pump type air-conditioning system including the flow path switching valve 1, refer to the above-mentioned Patent Documents 1 and 2 and the like.

[Structure of hexagonal valve body 10]
The hexagonal valve main body 10 has a tubular main valve housing 11 made of metal such as brass or stainless steel, and the first operating chamber 31 and the first operating chamber 31 and the first operating chamber 31 are sequentially connected to the main valve housing 11 from one end side (upper end side). One piston 21, a main valve chamber 12, a second piston 22, and a second operating chamber 32 are arranged. Each of the first and second pistons 21 and 22 is provided with a spring-loaded packing whose outer peripheral portion is in pressure contact with the inner peripheral surface of the main valve housing 11 in order to airtightly partition the main valve housing 11. ..

Specifically, the main valve housing 11 has a body portion 11c having a relatively large diameter, and is provided on a thick disk-shaped upper connecting lid 11d airtightly attached to the upper end opening of the body portion 11c. A first piston portion 11a made of a (relatively small diameter) pipe member is airtightly fixed to the central hole by brazing or the like, and the first piston 21 is arranged in the first piston portion 11a. Similarly, a second piston portion made of a (relatively small diameter) pipe member is provided in the central hole provided in the thick disk-shaped lower connecting lid 11e airtightly attached to the lower end opening of the body portion 11c. The 11b is airtightly fixed by brazing or the like, and the second piston 22 is arranged on the second piston portion 11b.

A thin disk-shaped upper end side lid member 11A defining a variable capacity first operating chamber 31 is airtightly fixed to the upper end of the main valve housing 11 (the first piston portion 11a) by brazing or the like. A thin disk-shaped lower end side lid member 11B defining a variable capacity second operating chamber 32 is airtightly fixed to the lower end of the main valve housing 11 (second piston portion 11b) by brazing or the like. There is. Ports p11 and p12 for introducing and discharging a high-pressure fluid (refrigerant) into the first operating chamber 31 and the second operating chamber 32 are attached to the upper end side lid member 11A and the lower end side lid member 11B (center), respectively. ing.

The main valve housing 11 (main valve chamber 12) is provided with a total of six ports.

Specifically, in the center of the left portion of the main valve chamber 12, for example, a metal first main valve seat (valve seat) 13 having a flat valve seat surface (right surface) is brazed to the main valve. Three ports (sequentially from the upper end side) consisting of pipe joints that are airtightly fixed to the body portion 11c (inner circumference) of the housing 11 and extend to the left on the valve seat surface of the first main valve seat 13. , Port pB, port pA, port pF) are vertically arranged (arranged in the axis O direction) and opened at substantially equal intervals.

Further, on the right center of the main valve chamber 12 (the position facing the first main valve seat 13, in other words, the position opposite to the axis O of the first main valve seat 13), the surface (left surface) thereof. ) Is a flat valve seat surface, for example, a metal second main valve seat (valve seat) 14 is airtightly fixed to (inner circumference) of the body portion 11c (inner circumference) of the main valve housing 11 by brazing or the like. On the valve seat surface of the second main valve seat 14, three ports (port pC, port pD, port pE in order from the upper end side) consisting of pipe joints extending to the right are arranged vertically (in the axis O direction). They are opened at approximately equal intervals (side by side).

Each port (port pB, port pA, port pF) provided on the first main valve seat 13 and each port (port pC, port pD, port pE) provided on the second main valve seat 14 face each other. In addition to being set at the position (opposite to the axis O), in this example, the diameters of the ports pA to pF provided on the first main valve seat 13 and the second main valve seat 14 are set to substantially the same diameter. Has been done.

In the main valve chamber 12, specifically, in the body portion 11c of the main valve housing 11, both side surfaces (left surface and right surface) are valve seat surfaces of the first main valve seat 13 and the second main valve seat 14. Sliding main valve bodies 15 having a rectangular cross section and having an annular sealing surface (detailed later), which are slidably brought into contact with each other, are arranged so as to be movable in the axis O direction (vertical direction). .. In this example, the dimensions of the main valve body 15 in the left-right direction and the front-rear direction are equal to or slightly larger than the outer diameters of the first piston portion 11a and the second piston portion 11b of the main valve housing 11.

The main valve body 15 is made of, for example, synthetic resin, and basically, the first slide valve body (high pressure side slide valve body) 15A on the first main valve seat 13 side (left side) and the second main valve seat 14 It has a two-part configuration with the second slide valve body (low pressure side slide valve body) 15B on the side (right side).

The first slide valve body 15A has a substantially cylindrical shape, and opens on the inner circumference of the left end portion (the end on the side opposite to the second slide valve body 15B side) to the valve seat surface of the first main valve seat 13. An inner collar 15a that defines an opening sized so that two adjacent ports (port pB and port pA, or port pA and port pF) of the three ports can be selectively communicated with each other. Is projected (toward the inside). The left end surface (end surface on the first main valve seat 13 side) of the inner flange-shaped portion 15a is the annular sealing surface 15s that is slidably brought into contact with the valve seat surface of the first main valve seat 13. There is. That is, in the present embodiment, the annular sealing surface 15s (formed around the opening of the first U-turn passage (high pressure side U-turn passage) 16A described later) of the first slide valve body 15A has a race track shape as an inner shape. Moreover, the outer shape is formed into a substantially rectangular shape (in particular, see FIGS. 5 to 7).

On the other hand, on the right side of the second slide valve body 15B (the side opposite to the side of the first slide valve body 15A), two adjacent ports of the three ports opened on the valve seat surface of the second main valve seat 14 are adjacent to each other. A second U-turn passage (low-pressure side U-turn passage) 16B is opened, which is composed of a bowl-shaped depression having a size capable of selectively communicating individual ports (port pC and port pD, or port pD and port pE). At the same time, the left surface of the second slide valve body 15B (the side surface on the side of the first slide valve body 15A) is fitted with an outer shape substantially the same as or slightly smaller than the inner shape of the tubular first slide valve body 15A. The convex portion 15b is extended (to the left).

The fitting convex portion 15b of the second slide valve body 15B is slidable on (the right side portion) of the tubular first slide valve body 15A (with the O-ring 18 sandwiched between the stepped portions provided between them). By being fitted inward, the inner peripheral surface of the first slide valve body 15A and the left end surface of the fitting convex portion 15b are adjacent to the three ports opened on the valve seat surface of the first main valve seat 13. A first U-turn passage (high-pressure side U-turn passage) 16A capable of selectively communicating two matching ports (port pB and port pA, or port pA and port pF) is defined, and a first slide valve is formed. The body 15A and the second slide valve body 15B are in the left-right direction (directions perpendicular to the axis O and provided on the first main valve seat 13) and the first port (port pB, port pA, port pF). 2 The directions in which the ports (port pC, port pD, port pE) provided on the main valve seat 14 face each other, that is, orthogonal to the valve seat surfaces of the first main valve seat 13 and the second main valve seat 14. It is said that it is slightly movable with respect to each other in the direction of movement) and is integrally movable in the vertical direction (axis O direction).

That is, in the present embodiment, the main valve body 15 has a first U-turn capable of selectively communicating two adjacent ports among the three ports opened on the valve seat surface of the first main valve seat 13. A second U-turn passage 16B capable of selectively communicating two adjacent ports among the three ports opened on the valve seat surface of the first slide valve body 15A having the passage 16A and the second main valve seat 14 is provided. It is composed of a pair with the second slide valve body 15B having the same, and the pair of first and second slide valve bodies 15A and 15B are opened in opposite directions by the first and second U-turn passages 16A and 16B, respectively. As described above (in other words, in the direction orthogonal to the valve seat surfaces of the first and second main valve seats 13 and 14), they are arranged back to back.

In the illustrated example, a step portion (inner peripheral step portion) formed on the inner circumference on the right end side of the first slide valve body 15A and a step portion (outer circumference) formed on the outer periphery of the fitting convex portion 15b of the second slide valve body 15B. An O-ring 18 as an annular sealing member is interposed between the stepped portion). Of course, a sealing member such as a lip seal may be used instead of the O-ring 18.

Therefore, in the portion of the first slide valve body 15A inside the O-ring 18 and on the side of the first main valve seat 13, high-pressure fluid (refrigerant) flows from the port (discharge side high-pressure port) pA via the first U-turn passage 16A. Introduced, the first U-turn passage 16A and the main valve chamber 12 are sealed by the O-ring 18 arranged between them.

Here, as can be clearly seen by referring to FIGS. 3 to 5 together with FIGS. 1 and 2, when viewed in the left-right direction (direction perpendicular to the axis O), the right side (third) side of the first slide valve body 15A. The pressure receiving area Sc on the two-slide valve body 15B side and the back pressure side) is made larger than the pressure receiving area Sa on the left side (first main valve seat 13 side).

More specifically, it is the projected area inside the O-ring 18 with respect to the plane perpendicular to the left-right direction, and is the first slide valve body 15A (right side) by the high-pressure refrigerant introduced into the first U-turn passage 16A. The projected area of the surface that receives pressure in the left direction (pressure receiving area Sc) is the projected area of the inner edge of the annular sealing surface 15s on the first main valve seat 13 side with respect to the plane perpendicular to the left-right direction (that is, here. The surface of the first slide valve body 15A (left surface) that receives pressure in the right direction due to the high-pressure refrigerant flowing through the port (inside the annular sealing surface 15s), which is approximately the same area as the projected area of the inner flange portion 15a. It is made larger than the projected area (pressure receiving area Sa).

As a result, when the high pressure refrigerant is introduced into the first U turn passage 16A via the port (discharge side high pressure port) pA, the pressure received from the first U turn passage 16A (high pressure refrigerant) (more specifically, the first U). The right side (annular seal surface) of the second slide valve body 15B due to the pressure received from the refrigerant (high pressure refrigerant) flowing through the turn passage 16A and the pressure received from the refrigerant (low pressure refrigerant) flowing through the second U turn passage 16B). Is pressed against the valve seat surface of the second main valve seat 14, and due to the difference in pressure receiving area (Sc-Sa) between the right side and the left side of the first slide valve body 15A, the first slide valve body 15A The left surface (annular seal surface 15s) of the first slide valve body 15A is pressed against the valve seat surface of the first main valve seat 13 by the differential pressure acting on the first main valve seat 13.

Further, in the present embodiment, in addition to the above configuration, when viewed in the left-right direction (direction perpendicular to the axis O), the right side of the first slide valve body 15A (the second slide valve body 15B side and the back). The outer shape of the pressure receiving area Sc on the compression side (that is, the outer shape of the O-ring 18) is made larger than the outer shape of the contact area Sb of the annular sealing surface 15s on the left side (first main valve seat 13 side). In other words, the outer shape of the pressure receiving area Sc on the right side of the first slide valve body 15A (that is, the outer shape of the O-ring 18) is set outside the annular sealing surface 15s.

As a result, the pressing force (surface pressure) of the left surface (annular sealing surface 15s) of the first slide valve body 15A against the valve seat surface of the first main valve seat 13 described above is substantially uniform.

It should be noted that, between the first slide valve body 15A and the second slide valve body 15B, for example, a stepped surface (leftward) forming a fitting convex portion 15b between the right surface of the first slide valve body 15A and the second slide valve body 15B. An urging member (ring-shaped leaf spring, compression coil spring, etc.) that urges the first slide valve body 15A and the second slide valve body 15B in opposite directions (to separate them) from each other (step surface). The left surface (annular seal surface) of the first slide valve body 15A is pressed (pressed) against the valve seat surface of the first main valve seat 13 and the right surface (of) of the second slide valve body 15B. The annular seal surface) may be pressed against the valve seat surface of the second main valve seat 14.

As described above, in the main valve body 15, the first slide valve body 15A and the second slide valve body 15B are integrally moved in the axis O direction, and the port pF as shown in FIG. 1 is provided. The port pB and the port pA are opened and communicated with each other through the first U-turn passage 16A of the first slide valve body 15A, and the port pE is opened and the port pC and the port pD are connected to each other through the second U-turn of the second slide valve body 15B. The cooling position (upper end position) communicating via the passage 16B and the port pB and the port pA and the port pF as shown in FIG. 2 are connected via the first U-turn passage 16A of the first slide valve body 15A. It is possible to selectively take a heating position (lower end position) in which the port pC is opened and the port pD and the port pE are communicated with each other via the second U-turn passage 16B of the second slide valve body 15B. ..

The first slide valve body 15A of the main valve body 15 is located directly above two of the three ports (port pB and port pA, or port pA and port pF) except when moving. The second slide valve body 15B of the main valve body 15 is located directly above two of the three ports (port pC and port pD, or port pD and port pE) except when moving. At this time, the valve seat surfaces of the first main valve seat 13 and the second main valve seat 14 are pressed to the left and right by the pressure from the high-pressure refrigerant introduced into the main valve body 15 (the first U-turn passage 16A). It is pressed against.

The first piston 21 and the second piston 22 are integrally movably connected by a connecting body 25, and the first slide valve body 15A and the second slide valve body 15B of the main valve body 15 are connected to the connecting body 25. The piston is fitted and supported in a state where it is slightly slidable in the left-right direction and is almost prevented from moving in the front-rear direction.

In this example, the connecting body 25 is composed of a pair of plate materials having the same size and shape, which are manufactured by, for example, press molding, and each plate material is formed in the left-right direction (first main valve seat 13 and second). The main valve seat 14 is arranged along the direction orthogonal to the valve seat surface (in other words, parallel to the plane orthogonal to the valve seat surface), and the pair of plate members are front and rear. They are arranged so as to face each other in the direction, and the main valve body 15 is sandwiched (in the front-rear direction) between the pair of plate members. Hereinafter, the plate material arranged on the front side of the main valve body 15 is referred to as a connecting plate 25A, and the plate material arranged on the rear side of the main valve body 15 is referred to as a connecting plate 25B.

More specifically, as can be clearly seen by referring to FIGS. 6 and 7 together with FIGS. 1 and 2, each of the connecting plates 25A and 25B is symmetrical with respect to the center line (symmetric line) extending in the front-rear direction from the center thereof. It is composed of a vertically long rectangular plate (here, the same width over the entire length of the top and bottom). At substantially the center (in the vertical direction) of each of the connecting plates 25A and 25B, the main valve body 15 (front side portion or rear side portion) is integrally movably engaged and supported in the axis O direction. A support plate portion 25c having a shape (that is, a substantially concave cross section) is formed along the outer periphery (front surface and upper and lower surfaces, or rear surface and upper and lower surfaces) of the valve body 15.

Above and below the support plate portion 25c in each of the connecting plates 25A and 25B, a connecting plate portion 25a extending to the first piston 21 or the second piston 22 is connected. Here, the connection plate portion 25a is formed in a step shape or a crank shape by bending or the like, and has an offset plate portion 25aa and a contact plate portion 25ab from the support plate portion 25c side. The offset plate portion 25aa of the connecting plate portion 25a in the connecting plate 25A on the front side is opened to the valve seat surfaces of the first main valve seat 13 and the second main valve seat 14 on the front side of the axis O, particularly in the left-right direction. The six ports pA to pF are arranged in a position avoiding the front side (in other words, a position offset forward from the six ports pA to pF), and the offset of the connecting plate portion 25a in the connecting plate 25B on the rear side. The plate portion 25aa has six ports pA to pF opened on the rear side of the axis O, particularly on the valve seat surfaces of the first main valve seat 13 and the second main valve seat 14 when viewed in the left-right direction. It is distributed at a position avoided (in other words, a position offset rearward from the six ports pA to pF). That is, in this example, when viewed in the left-right direction, the offset plate portions 25aa of the connection plate portions 25a of the pair of connecting plates 25A and 25B are opened in the valve seat surfaces of the first main valve seat 13 and the second main valve seat 14. Each port pA to pF (in the front-rear direction) is arranged apart from the diameter of each of the squeezed ports pA to pF, and is located between the offset plate portions 25aa of the connection plate portions 25a in the pair of connecting plates 25A and 25B. More specifically, in the cooling position (upper end position) shown in FIG. 1, the port pF and port pE located on the lower side, and in the heating position (lower end position) shown in FIG. 2, the port pB and port pC located on the upper side). It will be positioned (especially see FIG. 6).

Further, in the connecting plates 25A and 25B, the contact plate portion 25ab of the connecting plate portion 25a (a portion close to the first piston 21 or the second piston 22 and of the first main valve seat 13 and the second main valve seat 14). The portions (the portions that do not wrap with the ports pA to pF) opened on the valve seat surface are brought into contact with the connecting plate portions 25ab of the connecting plate portions 25a on the opposite side (opposed) connecting plates 25B and 25A. ing. In consideration of assembling property and the like described later, for example, the contact plate portion 25ab may be provided with unevenness or the like (alignment portion) in order to align the connecting plates 25A and 25B arranged to face each other. ..

At the upper and lower ends of each of the connecting plates 25A and 25B (the connecting plate portion 25a), the side opposite to the side of the connecting plates 25B and 25A arranged to face each other (the direction in which the supporting plate portion 25c having a substantially concave cross section is formed). A mounting leg portion 25b formed by being bent substantially 90 ° is provided, and a bolt 30 for connecting the connecting plates 25A and 25B to the first piston 21 or the second piston 22 is inserted into the mounting leg portion 25b. A screw hole 29 is provided for this purpose.

Further, in this example, the length of the connection plate portion 25a (offset plate portion 25aa + contact plate portion 25ab) of each of the connecting plates 25A and 25B in the vertical direction (axis O direction) is the first and the length of the main valve housing 11. It is shorter than the length of the second piston portions 11a and 11b. As a result, the upper connecting lid 11d of the main valve housing 11 (the outer peripheral portion of the first piston portion 11a in the main valve housing 11) becomes the support plate portion 25c (upper end side corner portion) of the connecting body 25 (each connecting plate 25A, 25B). It is a stopper that abuts and prevents the connecting body 25 (that is, the main valve body 15 fitted to the connecting body 25) from moving upward, and is a stopper in the lower connecting lid 11e (in the main valve housing 11). The outer peripheral portion of the two piston portions 11b abuts on the support plate portion 25c (lower end side corner portion) of the connecting body 25 (each connecting plate 25A, 25B) and fits into the connecting body 25 (that is, the connecting body 25). It is a stopper that prevents the combined main valve body 15) from moving downward.

In other words, in this example, the connecting body 25 (support plate portion 25c in each of the connecting plates 25A and 25B) is in contact with the upper connecting lid 11d or the lower connecting lid 11e of the main valve housing 11 to abut the main valve body 15. A stopper portion 25s for restricting movement in the vertical direction is provided.

As described above, by providing the connecting body 25 with the stopper portion 25s that restricts the movement of the main valve body 15, for example, the upper end side lid member 11A and the lower end side lid member 11B move upward of the first piston 21. Compared to the one that also serves as a stopper that prevents the movement of the second piston 22 and the downward movement of the second piston 22, the load applied to the first and second pistons 21 and 22 can be reduced, and the position of the main valve body 15 is restricted. The dimensional accuracy of the components of the first and second pistons 21 and 22 and the upper end side and lower end side lid members 11A and 11B can be relaxed. As described above, the upper end side lid member 11A and the lower end side lid member 11B move upward of the first piston 21 and downward of the second piston 22 (that is, the upper and lower parts of the main valve body 15). Of course, it may also serve as a stopper to prevent movement).

In this example, as described above, since the connecting plates 25A and 25B are made of plate materials having the same dimensions and the same shape, the two connecting plates 25A and 25B are arranged so as to face each other in the front-rear direction. The connecting plate portions 25ab of the connecting plate portions 25a and 25B of both connecting plates 25A and 25B are arranged in a combination in the opposite directions (specifically, upside down) so as to be in contact with each other, and each mounting is performed via the bolt 30. The leg portion 25b is fixed to the first piston 21 or the second piston 22. Then, the first slide valve body 15A and the second slide valve body 15B of the main valve body 15 are placed between the support plate portions 25c in the connecting plates 25A and 25B (a space having a substantially rectangular shape in the side view) (respectively in the left-right direction). By arranging (from), the first slide valve body 15A and the second slide valve body 15B of the main valve body 15 are slightly slidable in the left-right direction and are almost prevented from moving in the front-rear direction. It is fitted to the connecting body 25 (particularly, see FIG. 7).

The main valve body 15 fitted and supported by the connecting body 25 (a pair of connecting plates 25A and 25B) is the connecting plate 25A of the connecting body 25 as the first and second pistons 21 and 22 move back and forth. , 25B pushed by the upper portion or the lower portion (wide rectangular plane in the left-right direction) of the support plate portion 25c having a concave cross section (here, the first slide valve bodies 15A and the second of the main valve body 15). The upper and lower surfaces of the slide valve body 15B are pressed to move back and forth between the cooling position (upper end position) and the heating position (lower end position).

In this example, the case where the connecting body 25 is composed of a pair of plate materials (connecting plates 25A and 25B) having the same dimensions and the same shape is illustrated. For example, the connecting body 25 is made of one plate material. Of course, may be configured.

[Operation of hexagonal valve body 10]
Next, the operation of the hexagonal valve main body 10 having the above-described configuration will be described.

When the main valve body 15 arranged in the main valve housing 11 is in the heating position (lower end position) (second communication state as shown in FIG. 2), the first is via the four-way pilot valve 90 described later. When the 2 working chamber 32 is communicated with the port pA which is the discharge side high pressure port and the 1st working chamber 31 is communicated with the port pD which is the suction side low pressure port, the high pressure refrigerant is introduced into the 2nd working chamber 32. At the same time, the high-pressure refrigerant is discharged from the first operating chamber 31. Therefore, the pressure of the second operating chamber 32 on the other end side (lower end side) of the main valve chamber 12 becomes higher than the pressure of the first operating chamber 31 on the one end side (upper end side) of the main valve chamber 12, which is shown in FIG. As described above, the first and second pistons 21, 22 and the main valve body 15 move upward, and the stopper portion 25s of the connecting body 25 (support plate portions 25c in the connecting plates 25A and 25B) is the upper connecting lid 11d. The main valve body 15 takes a cooling position (upper end position) (first communication state as shown in FIG. 1).

As a result, the port pA and the port pB are communicated (via the first U turn passage 16A), the port pC and the port pD are communicated (via the second U turn passage 16B), and the port pE and the port pF are communicated with each other. Since the and are communicated (via the main valve chamber 12), the cooling operation is performed in the heat pump type air-conditioning system.

When the main valve body 15 is in the cooling position (upper end position) (first communication state as shown in FIG. 1), the first operating chamber 31 is connected to the discharge side high pressure port via the four-way pilot valve 90 described later. When the second operating chamber 32 is communicated with the port pD which is the suction side low pressure port while communicating with a certain port pA, a high pressure refrigerant is introduced into the first operating chamber 31 and a high pressure is applied from the second operating chamber 32. Refrigerant is discharged. Therefore, the pressure of the first operating chamber 31 on one end side (upper end side) of the main valve chamber 12 is higher than the pressure of the second operating chamber 32 on the other end side (lower end side) of the main valve chamber 12, which is shown in FIG. As a result, the first and second pistons 21, 22 and the main valve body 15 move downward, and the stopper portion 25s of the connecting body 25 (support plate portions 25c in the connecting plates 25A and 25B) is placed on the lower connecting lid. It is contact-locked to 11e, and the main valve body 15 takes a heating position (lower end position) (second communication state as shown in FIG. 2).

As a result, the port pA and the port pF are communicated (via the first U turn passage 16A), the port pE and the port pD are communicated (via the second U turn passage 16B), and the port pC and the port pB are communicated with each other. Since the and are communicated (via the main valve chamber 12), the heating operation is performed in the heat pump type heating / cooling system.

[Structure of four-way pilot valve 90]
The structure of the four-way pilot valve 90 as a pilot valve is well known, and as shown in the enlarged views of FIGS. 8A and 8B, electromagnetic waves are applied to the outer periphery of the base end side (left end side). A valve case 92 made of a cylindrical straight pipe to which a coil 91 is externally fitted and fixed is provided, and a suction element 95, a compression coil spring 96, and a plunger 97 are sequentially arranged in the valve case 92 from the base end side. Being present.

The left end of the valve case 92 is hermetically sealed to the flange-shaped portion (outer terrace portion) of the attractor 95 by welding or the like, and the attractor 95 is attached to the cover case 91A that covers the outer periphery of the electromagnetic coil 91 for energization excitation. It is fastened and fixed by the bolt 92B.

On the other hand, a filter-equipped lid member 98 having a thin tube insertion port (high-pressure introduction port a) for introducing a high-pressure refrigerant is airtightly attached to the right end opening of the valve case 92 by welding, brazing, caulking, or the like. The area surrounded by the lid member 98, the plunger 97, and the valve case 92 is the valve chamber 99. High-pressure refrigerant is introduced into the valve chamber 99 from the port (discharge side high-pressure port) pA via the high-pressure thin tube #a airtightly inserted into the thin tube insertion port (high-pressure introduction port a) of the lid member 98. It is supposed to be done.

Further, between the plunger 97 and the lid member 98 in the valve case 92, a valve seat 93 whose inner end surface is a flat valve seat surface is airtightly joined by brazing or the like. On the valve seat surface (inner end surface) of the above, ports b and ports (low pressure on the suction side) are sequentially connected to the first operating chamber 31 of the hexagonal valve main body 10 described above via a thin tube # b from the tip side (right end side). Port) The port c connected to the pD via the thin tube #c and the port d connected to the second operating chamber 32 via the thin tube #d are spaced apart from each other along the longitudinal direction (left-right direction) of the valve case 92. It is opened side by side and opened.

The plunger 97 arranged to face the suction element 95 is basically cylindrical, and is slidably arranged in the valve case 92 in the axial direction (direction along the center line L of the valve case 92). .. At the end of the plunger 97 opposite to the suction element 95 side, a valve body holder 94A that holds the valve body 94 slidably in the thickness direction on the free end side holds the base end portion together with the fitting 94B. It is attached and fixed by press fitting, caulking, etc. A leaf spring 94C that urges the valve body 94 in the direction of pressing the valve body 94 against the valve seat 93 (thickness direction) is attached to the valve body holder 94A. The valve body 94 of the valve seat 93 is in contact with the valve seat surface of the valve seat 93 in order to switch the communication state between the ports b, c, and d that open on the valve seat surface of the valve seat 93. The valve seat surface slides as the plunger 97 moves in the left-right direction.

Further, the valve body 94 has a size such that the adjacent ports bc and cd of the three ports b to d opened on the valve seat surface of the valve seat 93 can be selectively communicated with each other. A recess 94a is provided.

Further, the compression coil spring 96 is compressed between the suction element 95 and the plunger 97 to urge the plunger 97 in the direction of pulling it away from the suction element 95 (to the right in the figure). In the example, the valve seat 93 (the left end portion of the valve seat 93) is used as a stopper that prevents the plunger 97 from moving to the right. Needless to say, other configurations can be adopted as the configuration of this stopper.

The four-way pilot valve 90 is attached to an appropriate position such as the back side of the six-way valve main body 10 via the attachment 92A. Further, in the four-way pilot valve 90, the thin tube #c is connected to the port pD which is the low pressure port on the suction side, but the thin tube #c may be connected to the port pC through which the medium pressure refrigerant flows.

[Operation of four-way pilot valve 90]
In the four-way pilot valve 90 having the above-described configuration, when the energization of the electromagnetic coil 91 is turned off, the plunger 97 is subjected to the urging force of the compression coil spring 96 as shown in FIGS. 1 and 8 (A). The right end is pushed to a position where it abuts on the valve seat 93. In this state, the valve body 94 is located on the port b and the port c, and the port b and the port c communicate with each other by the recess 94a, and the port d and the valve chamber 99 communicate with each other. ) The high-pressure fluid flowing into pA is introduced into the second working chamber 32 via the high-pressure thin tube #a → valve chamber 99 → port d → thin tube # d → port p12, and the high-pressure fluid in the first working chamber 31 is ported. It flows from p11 → thin tube # b → port b → recess 94a → port c → thin tube # c → port (low pressure port on the suction side) pD and is discharged.

On the other hand, when the energization of the electromagnetic coil 91 is turned on, as shown in FIGS. Is attracted to (against the urging force of the compression coil spring 96). At this time, the valve body 94 is located on the port c and the port d, and the port c and the port d communicate with each other by the recess 94a, and the port b and the valve chamber 99 communicate with each other. The high-pressure fluid flowing into pA is introduced into the first working chamber 31 via the high-pressure thin tube #a → valve chamber 99 → port b → thin tube # b → port p11, and the high-pressure fluid in the second working chamber 32 is introduced into the port p12. → Thin tube # d → Port d → Recessed 94a → Port c → Thin tube # c → Port (low pressure port on the suction side) pD flows and is discharged.

Therefore, when the energization of the electromagnetic coil 91 is turned off, the main valve body 15 of the hexagonal valve main body 10 shifts from the heating position (second communication state) to the cooling position (first communication state), and the flow path as described above. While switching is performed, when the energization of the electromagnetic coil 91 is turned on, the main valve body 15 of the hexagonal valve main body 10 shifts from the cooling position (first communication state) to the heating position (second communication state), and is described above. The flow path is switched as described above.

As described above, in the six-way switching valve 1 of the present embodiment, the high-pressure fluid (port pA which is a high-pressure portion) flowing in the six-way switching valve 1 is switched by switching the energization of the electromagnetic four-way pilot valve 90 by ON / OFF. The main valve is moved by moving the main valve body 15 constituting the hexagonal valve main body 10 in the main valve chamber 12 by utilizing the differential pressure between the flowing fluid) and the low pressure fluid (the fluid flowing through the port pD which is the low pressure portion). The communication state between the six ports provided in the housing 11 is switched, and in the heat pump type heating / cooling system, it is possible to switch from the heating operation to the cooling operation and from the cooling operation to the heating operation.

[Action and effect of flow path switching valve 1]
As can be understood from the above description, in the flow path switching valve (six-way switching valve) 1 of the present embodiment, the first slide valve body (high pressure) is viewed in the left-right direction (direction perpendicular to the axis O). The outer shape of the pressure receiving surface (pressure receiving area Sc) on the second slide valve body (low pressure side slide valve body) 15B side (back pressure side) in the side slide valve body 15A is the annular sealing surface 15s (pair of) in the first slide valve body 15A. Since it is set larger than the outer shape of the contact area Sb), the contact surface (annular seal) of the first slide valve body 15A with the valve seat surface of the first main valve seat 13 is compared with, for example, the conventional flow path switching valve described above. Since the pressure distribution on the surface 15s) becomes substantially uniform, good sealing performance, operability, and stability can be ensured, and valve leakage can be effectively suppressed.

(Other Examples of First Embodiment)
In the first embodiment, the width direction of the main valve body 15 (in the illustrated example, the front-rear direction, perpendicular to the axis O, and the valve seat surfaces of the first and second main valve seats 13 and 14). The outer shape of the pressure receiving area Sc on the right side of the first slide valve body 15A is almost the same as the outer shape of the contact area Sb of the annular sealing surface 15s on the left side (specifically, slightly less than that). However, in order to further improve the sealing property, stability, etc., for example, as shown in FIGS. 9 to 11, the width direction dimension of the main valve body 15 is increased to increase the width direction of the first slide valve body. The outer shape of the pressure receiving area Sc on the right side in 15A may be expanded (in the width direction) to increase the margin for the outer shape of the contact area Sb of the annular sealing surface 15s on the left side.

(Second Embodiment)
12 to 15 show a second embodiment of the flow path switching valve (six-way switching valve) according to the present invention.

The flow path switching valve 2 of the second embodiment shown in the drawing has substantially the same configuration as the flow path switching valve 1 of the first embodiment described above except for the main valve body. Therefore, the parts corresponding to the respective parts of the flow path switching valve 1 of the first embodiment and the parts having the same functions are designated by a common reference numeral to omit the duplicate description, and in the following, the differences around the main valve body are omitted. The explanation will focus on the points.

In the flow path switching valve 2 of the illustrated embodiment, the annular sealing surface 15s provided on the left surface side (first main valve seat 13 side) of the first slide valve body 15A has a predetermined width around the opening of the first U-turn passage 16A. It is formed only (approximately the same width over the entire circumference).

Further, also in the present embodiment, the outer shape of the pressure receiving area Sc on the right side of the first slide valve body 15A (that is, the outer shape of the O-ring 18) is on the left side when viewed in the left-right direction (direction perpendicular to the axis O). It is made larger (over the entire circumference) than the outer shape of the contact area Sb of the annular sealing surface 15s.

In the flow path switching valve (six-way switching valve) 2 of the second embodiment, by adopting the above configuration, in addition to obtaining the same action and effect as the flow path switching valve 1 of the first embodiment. , The contact area between the first slide valve body 15A (annular seal surface 15s) and the first main valve seat 13 (valve seat surface) becomes smaller, and the first with respect to the first main valve seat 13 (valve seat surface). The pressing force (surface pressure) of the slide valve body 15A (annular sealing surface 15s) is increased, and the sealing property can be further improved. Further, since the pressure receiving area Sc on the right side of the first slide valve body 15A can be reduced, the size can be reduced and the degree of freedom in arranging other assembled parts can be increased.

(Third Embodiment)
16 to 19 show a third embodiment of the flow path switching valve (six-way switching valve) according to the present invention.

The flow path switching valve 3 of the third embodiment shown in the drawing has substantially the same configuration as the flow path switching valve 2 of the second embodiment described above except for the main valve body. Therefore, the parts corresponding to the respective parts of the flow path switching valve 2 of the second embodiment and the parts having the same functions are designated by a common reference numeral to omit the duplicate description, and in the following, the differences around the main valve body are omitted. The explanation will focus on the points.

In the flow path switching valve 3 of the illustrated embodiment, the upper end portion and the lower end portion (in other words, the axis O) of the annular sealing surface 15s provided on the left surface side (first main valve seat 13 side) of the first slide valve body 15A. At the center of the width direction in the direction (both ends in the direction or the moving direction), the height is the same as the annular seal surface 15s and the annular seal surface 15s (outer shape) is located in the vertical direction (along the axis O direction). A narrow, substantially rod-shaped convex portion 15t is continuously provided. In the illustrated example, the width of the substantially rod-shaped convex surface portion 15t is substantially the same as the width (the predetermined width) of the racetrack-shaped annular sealing surface 15s formed around the opening of the first U-turn passage 16A.

Further, also in the present embodiment, the outer shape of the pressure receiving area Sc on the right side of the first slide valve body 15A (that is, the outer shape of the O-ring 18) is on the left side when viewed in the left-right direction (direction perpendicular to the axis O). It is made larger (over the entire circumference) than the outer shape of the annular seal surface 15s and the convex surface portion 15t. In other words, the entire convex surface portion 15t connected to the annular seal surface 15s is provided so as to be located inside the pressure receiving area Sc on the right surface side.

For example, in the flow path switching valve 2 of the second embodiment described above, the first slide valve body 15A is the first main valve when switching the flow path by reducing the area of the annular sealing surface 15s of the first slide valve body 15A. When sliding on the valve seat surface of the seat 13, the annular sealing surface 15s of the first slide valve body 15A is likely to be caught in the port opened on the valve seat surface of the first main valve seat 13.

In the flow path switching valve (six-way switching valve) 3 of the third embodiment, by adopting the above configuration, in addition to obtaining the same action and effect as the flow path switching valve 2 of the second embodiment. The substantially rod-shaped convex surface portion 15t connected to the annular seal surface 15s makes it easier for the annular seal surface 15s of the first slide valve body 15A to get over the port opened in the valve seat surface of the first main valve seat 13. It is possible to effectively prevent the annular sealing surface 15s of the first slide valve body 15A from being caught on the port.

(Fourth Embodiment)
FIG. 20 shows a fourth embodiment of the flow path switching valve (six-way switching valve) according to the present invention.

The flow path switching valve 4 of the fourth embodiment shown in the drawing has substantially the same configuration as the flow path switching valve 3 of the third embodiment described above except for the main valve body. Therefore, the parts corresponding to the respective parts of the flow path switching valve 3 of the third embodiment and the parts having the same functions are designated by a common reference numeral to omit the duplicate description, and in the following, the differences around the main valve body are omitted. The explanation will focus on the points.

In the flow path switching valve 4 of the illustrated embodiment, the outer shape of the pressure receiving area Sc on the right side of the first slide valve body 15A (that is, the outer shape of the O-ring 18) when viewed in the left-right direction (direction perpendicular to the axis O). ) Is a race track type, and a part of the outer shape of the pressure receiving area Sc is made smaller than the tip portion of the convex surface portion 15t on the left surface side. In other words, the root portion (the portion adjacent to the annular seal surface 15s) of the convex surface portion 15t connected to the annular seal surface 15s is located inside the pressure receiving area Sc on the right surface side, and the tip portion (annular portion) of the convex surface portion 15t. A portion (a portion separated from the sealing surface 15s) is provided so as to be located outside the pressure receiving area Sc on the right surface side.

For example, in the flow path switching valve 3 of the third embodiment described above, an O-ring as a seal member arranged between the first slide valve body 15A and the second slide valve body 15B (sliding surface gap). 18 becomes a deformed shape, and the difficulty of mold design and assembly work becomes high. Further, the tip portion of the rod-shaped convex surface portion 15t extending in the vertical direction is a region where the pressure distribution is small or hardly occurs.

In the flow path switching valve (six-way switching valve) 4 of the fourth embodiment, by adopting the above configuration, in addition to obtaining the same action and effect as the flow path switching valve 3 of the third embodiment. , The shape of the O-ring 18 arranged between the first slide valve body 15A and the second slide valve body 15B (sliding surface gap) can be simplified, and the annular sealing surface 15s and the convex surface portion having a pressure distribution can be simplified. Since the root portion of 15t is effectively pressed against the valve seat surface of the first main valve seat 13, the sealing property and the like can be further improved.

In the flow path switching valves 1 to 4 of the above-described embodiment, the configuration in which the main valve body 15 is driven in the main valve chamber 12 by using the four-way pilot valve 90 has been described. May be used to drive the main valve body 15 in the main valve chamber 12.

Further, in the flow path switching valves 1 to 4 of the above-described embodiment, the six-way switching valve in the heat pump type air-conditioning system has been described as an example, but the number and positions of the ports provided in the main valve housing 11 (main valve chamber 12) have been described. The configuration and shape of the main valve housing 11, the configuration and shape of the main valve body 15 and the connecting body 25 arranged in the main valve housing 11 (main valve chamber 12) are not limited to the illustrated examples. Of course, it is needless to say that it can be applied to a multi-way switching valve other than the six-way switching valve.

Further, it goes without saying that the flow path switching valves 1 to 4 of the present embodiment can be incorporated not only in the heat pump type air-conditioning system but also in other systems, devices and devices.

1 Flow path switching valve (six-way switching valve) (first embodiment)
2 Flow path switching valve (six-way switching valve) (second embodiment)
3 Flow path switching valve (six-way switching valve) (third embodiment)
4 Flow path switching valve (six-way switching valve) (4th embodiment)
10 Hexagonal valve body 11 Main valve housing 11A Upper end side lid member 11B Lower end side lid member 11a First piston part 11b Second piston part 11c Body part 12 Main valve chamber 13 First main valve seat (valve seat)
14 Second main valve seat (valve seat)
15 Main valve body 15A 1st slide valve body (high pressure side slide valve body)
15B 2nd slide valve body (low pressure side slide valve body)
15a Inner collar-shaped portion 15b of the first slide valve body Fitting convex portion 15s of the second slide valve body An annular sealing surface 15t of the first slide valve body (high pressure side slide valve body) Convex surface portion 16A 1st U-turn passage (high pressure side) U-turn passage)
16B 2nd U-turn passage (low voltage side U-turn passage)
18 O-ring (annular seal member)
21 First piston 22 Second piston 25 Connecting body 25A, 25B Pair of connecting plates 31 First operating chamber 32 Second operating chamber 90 Four-way pilot valve pA, pB, pC, pD, pE, pF port

Claims (8)

The main valve housing that defines the main valve chamber and
A first main valve seat, which is arranged in the main valve chamber and has a valve seat surface in which a plurality of ports are opened,
A second main valve seat, which is arranged in the main valve chamber on the opposite side of the first main valve seat with respect to the axis of the main valve chamber and has a valve seat surface in which a plurality of ports are opened, and a second main valve seat.
A high-pressure side slide valve body having a high-pressure side U-turn passage into which a relatively high-pressure fluid is introduced and slidable on the valve seat surface of the first main valve seat, and a relatively low-pressure fluid are introduced. It is configured to have a low-pressure side U-turn passage to be formed and a pair of slide valve bodies of a low-pressure side slide valve body slidable on the valve seat surface of the second main valve seat. It is equipped with a main valve body that is movable in the axial direction.
The pair of slide valve bodies are integrally movable in the axial direction and are slidable with each other in the direction perpendicular to the axis.
A flow path switching valve that allows communication between the plurality of ports of the first main valve seat and the second main valve seat to be switched by moving the main valve body in the main valve chamber. There,
In the pair of slide valve bodies, an annular sealing surface facing the valve seat surface is formed around the opening of the high pressure side U-turn passage in the high pressure side slide valve body.
A flow path characterized in that the outer shape of the pressure receiving surface on the low pressure side slide valve body side of the high pressure side slide valve body is set to be larger than the outer shape of the annular seal surface when viewed in a direction perpendicular to the axis line. Switching valve. The flow path switching valve according to claim 1, wherein the annular sealing surface is formed only in a predetermined width around an opening of the high-pressure side U-turn passage. The first or second aspect of the present invention, wherein a convex surface portion having the same height as the annular seal surface and narrower than the annular seal surface is continuously provided at the axial end portion of the annular seal surface. Flow switching valve. The third aspect of the present invention, wherein the entire convex surface portion is provided so as to be located inside the pressure receiving surface on the low pressure side slide valve body side when viewed in a direction perpendicular to the axis line. Flow switching valve. When viewed in a direction perpendicular to the axis, the root portion of the convex surface portion is located inside the pressure receiving surface on the low pressure side slide valve body side, and the tip portion of the convex surface portion is on the low pressure side slide valve body side. The flow path switching valve according to claim 3, wherein the flow path switching valve is provided so as to be located outside the pressure receiving surface of the above. The flow path switching valve according to any one of claims 3 to 5, wherein the convex surface portion is provided at least at a central portion in the width direction of the annular seal surface. An annular seal member is arranged between the high pressure side slide valve body and the low pressure side slide valve body, and the outer shape of the seal member is set to be larger than the outer shape of the annular seal surface. The flow path switching valve according to any one of claims 1 to 6. The high-pressure side slide valve body has a tubular shape, and a fitting convex portion slidably fitted in the high-pressure side slide valve body is provided on one side surface of the low-pressure side slide valve body. By internally fitting the fitting convex portion into the side slide valve body, the high pressure side U-turn passage is defined by the inner peripheral surface of the high pressure side slide valve body and the end surface of the fitting convex portion, and the high pressure side U-turn passage is defined. The high-pressure side slide valve body and the low-pressure side slide valve body are integrally movable in the axial direction and slidable to each other in a direction perpendicular to the axis, and the low-pressure side slide. The flow path switching valve according to any one of claims 1 to 7, wherein the low-pressure side U-turn passage is provided on the other side surface of the valve body.

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