JP2020029920A - Channel selector valve - Google Patents

Abstract

To provide a channel selector valve that can secure preferable sealability, operating property and stability and effectively suppress valve leakage.SOLUTION: In a channel selector valve, an outer shape of a pressure receiving surface (pressure receiving area Sc) on a side (back pressure side) of a second slide valve element (low-pressure side slide valve element) 15B in a first slide valve element (high-pressure side slide valve element) 15A is set to be larger than an outer shape of an annular seal surface 15s (opposite contact area Sb thereof) in the first slide valve element 15A, in horizontal direction (direction perpendicular to axis line O) view.SELECTED DRAWING: Figure 5

Description

  The present invention relates to a flow path switching valve that switches a flow path by moving a valve element, and for example, relates to a flow path switching valve suitable for performing a flow path switching in a heat pump type cooling / heating system or the like.

  Generally, a heat pump type cooling / heating system such as a room air conditioner includes a flow path switching valve (four-way switching) as flow path (flow direction) switching means in addition to a compressor, an outdoor heat exchanger, an indoor heat exchanger, an expansion valve, and the like. Valves and a six-way switching valve), 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 cooling / heating system or the like as described above, one in which one slide-type main valve element is slidably disposed in a valve body (main valve housing) is well known. However, for example, as described in Patent Document 2, a device integrally using a plurality of slide-type valve elements has already been proposed, as disclosed in Patent Document 2, for example.

  The slide type flow path switching valve (six-way switching valve) includes three cylindrical main valve housings each defining a main valve chamber, and three main valve housings (main valve chambers) on opposite sides of the axis of the main valve housing (main valve chamber). A main valve seat having a valve seat surface with an opened port, and a port movably disposed in the main valve chamber in the axial direction, and slidably contacting the valve seat surface. A main valve element having a slidable main valve element, wherein the main valve element has a first U-turn passage (high-pressure U-turn passage) for selectively communicating two of the three ports. A second slide valve element having a second U-turn passage (low-pressure U-turn path) for selectively communicating one slide valve element (high-pressure side slide valve element) with two of the other three ports. (Low-pressure side slide valve element). The respective U-turn passages are arranged in a back-to-back state so as to open in opposite directions, and the slide valve bodies are integrally movable in the axial direction and slide with each other in a direction perpendicular to the axis. The main valve body is movable in the main valve chamber, so that the ports (flow paths) communicating with each other are switched via the U-turn passage.

  In the slide type flow path switching valve (six-way switching valve) described above, a fluid having a high pressure relative to the first U-turn passage (high-pressure U-turn passage) of the first slide valve element (high-pressure side slide valve element) is used. Is introduced, a relatively low-pressure fluid is introduced into a second U-turn passage (low-pressure side U-turn passage) of the second slide valve body (low-pressure side slide valve body), and a high-pressure side slide valve body and a 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 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 three ports, that is, the opening area of the high pressure side U-turn passage of the high pressure side slide valve element.

  Therefore, when the high-pressure refrigerant is introduced into the high-pressure U-turn passage and a part of the high-pressure refrigerant introduced into the high-pressure U-turn passage is filled in the pressure chamber, the pressure received from (the high-pressure refrigerant of) the pressure chamber 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.

JP-A-8-170864 JP 2018-044666 A

  However, in the conventional flow path switching valve described in Patent Document 2 and the like, as described above, the opening area of the high-pressure side U-turn passage of the high-pressure side slide valve body causes the pressure chamber side of the high-pressure side slide valve body to be closed. Although the pressure receiving area on the (back pressure side) is set to be larger (wider), the contact area (annular sealing surface) of the high pressure side slide valve body with the valve seat surface of the main valve seat is higher in the high pressure side slide valve body. 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 element becomes non-uniform, resulting in sealing and operability. , Stability may be reduced.

  The present invention has been made in view of the above circumstances, and a purpose thereof is to provide a flow path switching valve that can ensure good sealing performance, operability, and stability, and that can effectively suppress valve leakage. To provide.

  In order to achieve the above object, a flow path switching valve according to the present invention is basically provided with a main valve housing defining a main valve chamber, and a plurality of ports arranged in the main valve chamber and having a plurality of ports opened. A first main valve seat having a closed valve seat surface, and a plurality of ports disposed 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. A high pressure side slide valve having a second main valve seat having a valve seat surface, a high pressure side U-turn passage through which a relatively high pressure fluid is introduced, and being slidable on the valve seat surface of the first main valve seat. And a pair of slide valve bodies of a low pressure side slide valve body having a low pressure side U-turn passage through which a relatively low pressure fluid is introduced and slidable on the valve seat surface of the second main valve seat. And a main valve body arranged so as to be movable in the axial direction in the main valve chamber. Wherein the pair of slide valve bodies are integrally movable in the axial direction and slidable with each other in a direction perpendicular to the axis, and the main valve in the main valve chamber. A flow path switching valve configured to switch communication between the plurality of ports of each of the first main valve seat and the second main valve seat by moving a body, wherein the pair of slide valves The body has an annular sealing surface that is in contact with the valve seat surface around the opening of the high-pressure side U-turn passage in the high-pressure side slide valve body, and is formed in a direction perpendicular to the axis. The outer shape of the pressure-receiving surface of the high-pressure side slide valve element on the side of the low-pressure side slide valve element is set to be larger than the outer shape of the annular sealing surface.

  In a preferred aspect, 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 aspect, a convex portion having the same height as the annular sealing surface and a width smaller than the annular sealing surface is continuously provided at the axial end portion of the annular sealing surface.

  In a further preferred aspect, when viewed in a direction perpendicular to the axis, the entirety of 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.

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

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

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

  In another preferred aspect, the high-pressure side slide valve body has a cylindrical shape, and a fitting protrusion that is slidably fitted to the high-pressure side slide valve body on one side surface of the low-pressure side slide valve body. Is provided, and the fitting projection is internally fitted to the high-pressure side slide valve element, so that the high-pressure side U-turn passage is formed by the inner peripheral surface of the high-pressure side slide valve element and the end face of the fitting projection. The high pressure side slide valve element and the low pressure side slide valve element 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, when viewed in a direction perpendicular to the axis, 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 in the high pressure side slide valve body. Since it is set to be 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 element with the valve seat surface of the main valve seat is substantially smaller than, for example, the conventional flow path switching valve described above. Since it is uniform, good sealing performance, operability, and stability can be ensured, and valve leakage can be effectively suppressed.

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

FIG. 3 is a longitudinal sectional view showing a first communication state (at the time of cooling operation) of the first embodiment of the flow path switching valve according to the present invention. FIG. 4 is a longitudinal sectional view showing a second communication state (at the time of a heating operation) of the first embodiment of the flow path switching valve according to the present invention. FIG. 2 is an enlarged vertical cross-sectional view of a main part of the flow path switching valve shown in FIG. 1. FIG. 5 is a sectional view taken along the line VV of FIG. 3. FIG. 4 is a sectional view taken along line WW of FIG. 3. FIG. 2 is a sectional view taken along the line U-U in FIG. 1. FIG. 2 is a perspective view showing a main valve body and a connection body of the first embodiment of the flow path switching valve according to the present invention. It is a figure which expands and shows the four-way pilot valve used for the flow-path switching valve which concerns on this invention, (A) is a 1st communication state (at the time of cooling operation) (at the time of energization OFF), (B) is a 2nd communication. FIG. 4 is a longitudinal sectional view showing states (at the time of heating operation) (at the time of energization ON). The principal part expansion longitudinal cross-sectional view which expands and shows the principal part of the other example of the flow path switching valve shown in FIG. FIG. 10 is a sectional view taken along the line VV of FIG. 9. FIG. 10 is a sectional view taken along the line WW of FIG. 9. The principal part expansion longitudinal cross-sectional view which expands and shows the principal part of 2nd Embodiment of the flow-path switching valve which concerns on this invention. Sectional drawing which follows the VV arrow line of FIG. FIG. 13 is a sectional view taken along line WW of FIG. 12. The perspective view which shows the main valve body and connection body of 2nd Embodiment of the flow-path switching valve which concerns on this invention. The principal part expansion longitudinal cross-sectional view which expands and shows the principal part of 3rd Embodiment of the flow-path switching valve which concerns on this invention. FIG. 17 is a sectional view taken along the line VV of FIG. 16. FIG. 17 is a sectional view taken along the line WW of FIG. 16. FIG. 9 is a perspective view showing a main valve body and a connection body of a third embodiment of the flow path switching valve according to the present invention. FIG. 17 is a cross-sectional view of a fourth embodiment of the flow path switching valve according to the present invention, taken along line WW of FIG. 16.

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

(1st Embodiment)
1 and 2 are longitudinal sectional views showing a first embodiment of a flow path switching valve (a six-way switching valve) according to the present invention. FIG. 1 shows a first communication state (at the time of cooling operation), and FIG. FIG. 8 is a diagram showing a second communication state (during a heating operation).

  In this specification, descriptions indicating positions and directions such as up and down, left and right, front and back, etc. are provided for convenience according to the drawings in order to avoid complicating the description, and are actually incorporated in a heat pump type cooling / heating system or the like. It does not necessarily indicate the position and direction in the closed state.

  In each of the drawings, a gap formed between members, a separation distance between members, and the like are larger than dimensions of each constituent member for easy understanding of the invention and for convenience of 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 cooling / heating system, and basically includes a cylinder type six-way valve body 10 and a single electromagnetic valve as a pilot valve. And a four-way pilot valve 90. The six ports provided in the flow path switching valve 1 of the present embodiment are assigned the same reference numerals corresponding to the respective ports pA to pF of the six-way switching valve described in Patent Documents 1 and 2. Have been. For the basic configuration of the heat pump type cooling and heating system including the flow path switching valve 1, refer to the above-mentioned Patent Documents 1 and 2.

[Configuration of Six-Way Valve Body 10]
The six-way valve main body 10 has a cylindrical main valve housing 11 made of metal such as brass or stainless steel, and the main valve housing 11 is provided with a first working chamber 31 and a first working chamber 31 in order from one end side (upper end side). A first piston 21, a main valve chamber 12, a second piston 22, and a second working 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 pressed against the inner peripheral surface of the main valve housing 11 in order to partition the main valve housing 11 in an airtight manner. .

  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 connection lid 11d that is hermetically attached to an upper end opening of the body portion 11c. A first piston portion 11a made of a pipe member (having a relatively small diameter) is air-tightly 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 pipe member (having a relatively small diameter) is provided in a center hole provided in a thick disc-shaped lower connection lid 11e which is hermetically attached to a lower end opening of the body portion 11c. 11b is hermetically fixed by brazing or the like, and the second piston 22 is disposed on the second piston portion 11b.

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

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

  Specifically, in the center of the left part of the main valve chamber 12, a first main valve seat (valve seat) 13 made of, for example, metal whose surface (right surface) is a flat valve seat surface is formed by brazing or the like. Three ports (in the order from the upper end side) formed of pipe joints which are airtightly fixed to (the inner periphery of) the body portion 11c of the housing 11 and extend leftward on the valve seat surface of the first main valve seat 13 , Port pB, port pA, and port pF) are vertically arranged (arranged in the direction of the axis O) and are opened at substantially equal intervals.

  The right side center (the position facing the first main valve seat 13, in other words, the position on the opposite side of the first main valve seat 13 with respect to the axis O) of the main valve chamber 12 has its surface (left surface). ) Has a flat valve seat surface, for example, a metal second main valve seat (valve seat) 14 is hermetically fixed to (the inner periphery of) the body portion 11c 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 (ports pC, port pD, and port pE) consisting of pipe joints extending rightward are arranged vertically (in the direction of the axis O). The openings are arranged at substantially equal intervals.

  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 this example, the ports pA to pF provided in the first main valve seat 13 and the second main valve seat 14 are set to have substantially the same diameter. Have been.

  In the main valve chamber 12, specifically, in the body 11 c of the main valve housing 11, both side surfaces (left and right surfaces) are valve seat surfaces of the first main valve seat 13 and the second main valve seat 14. A sliding main valve body 15 having an annular sealing surface (described later in detail) and having a rectangular cross section is movably arranged in the direction of the axis O (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, a synthetic resin, and basically includes a first slide valve body (high-pressure side slide valve body) 15A on the first main valve seat 13 side (left side) and a second main valve seat 14. And a 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 is opened on the valve seat surface of the first main valve seat 13 on the inner periphery of the left end (the end opposite to the second slide valve body 15B). Inner flange portion 15a defining an opening large enough to selectively communicate two adjacent ports (port pB and port pA or port pA and port pF) among the three ports. Is protruding (inward). The left end surface (the end surface on the first main valve seat 13 side) of the inner flange portion 15a is the annular sealing surface 15s which is slidably brought into contact with the valve seat surface of the first main valve seat 13. I have. That is, in the present embodiment, the inner shape of the annular seal surface 15s (formed around the opening of the first U-turn passage (high-pressure U-turn passage) 16A described later) of the first slide valve body 15A has a racetrack shape. Further, the outer shape is formed in a substantially rectangular shape (particularly, see FIGS. 5 to 7).

  On the other hand, on the right side of the second slide valve element 15B (opposite to the first slide valve element 15A side), two adjacent ports among the three ports opened on the valve seat surface of the second main valve seat 14 are arranged. A second U-turn passage (low-pressure-side U-turn passage) 16B is formed of a bowl-shaped recess having a size such that the ports (ports pC and pD or ports pD and port pE) can be selectively communicated. In addition, a fitting having an outer shape that is substantially the same as or slightly smaller than the inner shape of the cylindrical first slide valve body 15A is fitted on the left surface (side surface on the side of the first slide valve body 15A) of the second slide valve body 15B. The mating projection 15b extends (to the left).

  The fitting projection 15b of the second slide valve element 15B is slidably slidable (on the right side of the cylindrical first slide valve element 15A) (with the O-ring 18 interposed between the step portions provided therebetween). By being internally fitted, 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 one of 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 for selectively communicating two matching ports (port pB and port pA or port pA and port pF) and a first slide valve are provided. The body 15 </ b> A and the second slide valve body 15 </ b> B are connected to each other (ports (port pB, port pA, port pF) provided in the first main valve seat 13 in a left-right direction (a direction perpendicular to the axis O). Each port provided on the two main valve seats 14 ( Port pC, port pD, and port pE) are slightly movable relative to each other in a direction in which the first main valve seat 13 and the second main valve seat 14 are orthogonal to each other. In addition, they are integrally movable vertically (in the direction of the axis O).

  That is, in the present embodiment, the main valve body 15 is a first U-turn that can selectively communicate 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 adjacent two of the three ports opened in the valve seat surface of the first slide valve element 15A having the passage 16A and the second main valve seat 14 is provided. And a pair of first and second slide valve bodies 15A and 15B, the first and second U-turn passages 16A and 16B open in opposite directions. As described above (in other words, in a 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 periphery on the right end side of the first slide valve body 15A and a step portion (outer periphery) formed on the outer periphery of the fitting projection 15b of the second slide valve body 15B. An O-ring 18 as an annular sealing member is interposed between the O-ring 18 and the step portion. Note that a seal member such as a lip seal may be used instead of the O-ring 18.

  Therefore, a portion of the first slide valve body 15A inside the O-ring 18 and on the first main valve seat 13 side receives high-pressure fluid (refrigerant) 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 (sealed) by the O-ring 18 disposed therebetween.

  Here, as can be understood by referring to FIGS. 3 to 5 together with FIGS. 1 and 2, when viewed in the left-right direction (the direction perpendicular to the axis O), the right side (the first The pressure receiving area Sc on the two-slide valve body 15B side (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 a projected area inside the O-ring 18 with respect to a plane perpendicular to the left-right direction, and the right side of the first slide valve body 15A (high-pressure refrigerant) introduced by the high-pressure refrigerant introduced into the first U-turn passage 16A. Is the projected area of the surface receiving 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 a plane perpendicular to the left-right direction (that is, in this case, (The area approximately equal to the projected area of the inner flange portion 15a), and the surface of the first slide valve body 15A (left surface) which receives the rightward pressure by the high-pressure refrigerant flowing through the port (inside the annular sealing surface 15s). It is larger than the projection area (pressure receiving area Sa).

  Thereby, 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 (more specifically, the first U-pressure) received from (the high-pressure refrigerant of) the first U-turn passage 16A. Due to the pressure difference between 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 (the annular sealing surface of the right surface of the second slide valve body 15B). Is pressed against the valve seat surface of the second main valve seat 14, and the first slide valve body 15A is caused by the difference (Sc-Sa) in the pressure receiving area between the right side and the left side of the first slide valve body 15A. , The left surface (the annular sealing surface 15 s) of the first slide valve body 15 </ b> A is pressed against the valve seat surface of the first main valve seat 13.

  In addition, in the present embodiment, in addition to the above configuration, when viewed in the left-right direction (the direction perpendicular to the axis O), the right side (the second slide valve body 15B side) of the first slide valve body 15A The outer shape of the pressure receiving area Sc on the pressure 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 seal surface 15s on the left side (the 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 seal surface 15s.

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

  In addition, between the first slide valve body 15A and the second slide valve body 15B, for example, a step surface (leftward facing) that forms the fitting projection 15b of the right side of the first slide valve body 15A and the second slide valve body 15B. A biasing member (ring-shaped leaf spring, compression coil spring, etc.) for biasing the first slide valve body 15A and the second slide valve body 15B in mutually opposite directions (directions of separation) between the first slide valve body 15A and the second slide valve body 15B. This allows the left side (the annular sealing surface) of the first slide valve body 15A to be pressed against (pressed against) the valve seat surface of the first main valve seat 13 and the right side of the second slide valve body 15B. The annular seal surface) may be pressed (pressed) against the valve seat surface of the second main valve seat 14.

  As described above, the main valve element 15 is configured such that the first slide valve element 15A and the second slide valve element 15B are integrally moved in the direction of the axis O, and a port pF as shown in FIG. The port pB is opened and the port pB is connected to the port pA via 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 the second U-turn of the second slide valve body 15B. A cooling position (upper end position) communicating through the passage 16B and a port pB as shown in FIG. 2 and opening the port pA and the port pF through the first U-turn passage 16A of the first slide valve body 15A, as shown in FIG. A heating position (lower end position) in which the port pC is opened and the port pD and the port pE are communicated via the second U-turn passage 16B of the second slide valve element 15B while communicating with the port pC. ) Is a to obtain selective to take.

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

  The first piston 21 and the second piston 22 are connected by a connecting body 25 so as to be integrally movable. The connecting body 25 is connected to a first slide valve body 15A and a second slide valve body 15B of the main valve body 15. Are fitted and supported in a state where they are slightly slidable in the left-right direction and substantially prevented from moving in the front-rear direction.

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

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

  A connecting plate 25a extending to the first piston 21 or the second piston 22 is connected above and below the support plate 25c in each of the connecting plates 25A and 25B. 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 connection plate portion 25a in the front connection plate 25A is opened on the valve seat surface of the first main valve seat 13 and the second main valve seat 14 in front of the axis O, particularly when viewed in the left-right direction. Are located at positions avoiding the six ports pA to pF on the front side (in other words, positions offset forward from the six ports pA to pF), and offset of the connection plate portion 25a in the rear connection plate 25B. The plate portion 25aa is located on the rear side of the axis O, particularly, the six ports pA to pF opened 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. (In other words, positions offset backward 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 connection plates 25A and 25B are opened on the valve seat surfaces of the first main valve seat 13 and the second main valve seat 14. The ports pA to pF are disposed apart from each other (in the front-rear direction) from the apertures of the obstructed ports pA to pF and between the offset plate portions 25aa of the connection plate portions 25a in the pair of connection plates 25A and 25B. More specifically, the ports pF and pE located on the lower side in the cooling position (upper end position) shown in FIG. 1 and the ports pB and pC located on the upper side in the heating position (lower end position) shown in FIG. It will be located (especially, see FIG. 6).

  Further, the contact plate portion 25ab of the connection plate portion 25a in the connection plates 25A and 25B (the portion close to the first piston 21 or the second piston 22 and the first main valve seat 13 and the second main valve seat 14) Portions that do not overlap with the ports pA to pF that are opened on the valve seat surface) are brought into contact with the contact plate portion 25ab of the connection plate portion 25a of the connection plates 25B and 25A on the opposite side (disposed). ing. In consideration of assemblability and the like described later, for example, unevenness or the like (positioning portion) may be provided on the contacting plate portion 25ab in order to mutually position the connecting plates 25A and 25B arranged opposite to each other. .

  The upper and lower ends of the connection plates 25A and 25B (the connection plate portions 25a thereof) are opposite to the connection plates 25B and 25A that are opposed to each other (the direction in which the support plate portion 25c having a substantially concave cross section is formed). And a mounting bolt 25 for connecting the connecting plate 25A, 25B to the first piston 21 or the second piston 22 is inserted into the mounting leg 25b. Screw holes 29 are formed through the holes.

  In this example, the length of the connection plate 25a (offset plate 25aa + contact plate 25ab) of the connection plates 25A and 25B in the up-down direction (the direction of the axis O) is the first of the main valve housing 11 and The length is shorter than the length of the second piston portions 11a and 11b. Thereby, the upper connection lid 11d of the main valve housing 11 (the outer peripheral portion of the first piston portion 11a) is attached to the (upper end side corner portion) of the support plate portion 25c of the connection body 25 (the respective connection plates 25A and 25B). The stopper 25 serves as a stopper that comes into contact with the connection body 25 (that is, the main valve body 15 fitted to the connection body 25) and prevents the upward movement of the connection body 25. The outer peripheral portion of the two-piston portion 11b abuts on (the lower-end corner of) the support plate portion 25c of the connecting body 25 (each of the connecting plates 25A and 25B), and fits into the connecting body 25 (that is, the connecting body 25). It is a stopper that prevents the main valve body 15) that has been fitted to move downward.

  In other words, in this example, the connecting member 25 (the supporting plate portion 25c of each of the connecting plates 25A and 25B thereof) abuts on the upper connecting lid 11d or the lower connecting lid 11e of the main valve housing 11 and the main valve body 15 A stopper 25s for regulating movement in the vertical direction is provided.

  As described above, the stopper 25s that regulates the movement of the main valve body 15 is provided in the connecting body 25, so that, for example, the upper end side lid member 11A and the lower end side lid member 11B move upward of the first piston 21. As compared with a stopper that also 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 and lower lid members 11A and 11B can be reduced. As described above, the upper end side lid member 11A and the lower end side lid member 11B move upward in the first piston 21 and downward in the second piston 22 (that is, the upper and lower sides of the main valve body 15). Needless to say, the stopper may also serve as a stopper for preventing movement).

  In this example, as described above, since each of the connecting plates 25A and 25B is made of a plate material having the same size and the same shape, the two connecting plates 25A and 25B are arranged facing each other in the front-rear direction, The connecting plate portions 25ab of the connecting plate portions 25a of the two connecting plates 25A and 25B are arranged in a reverse direction (specifically, upside down) so as to abut each other, and are mounted via bolts 30. The leg 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 inserted between the support plate portions 25c of each of the connection plates 25A and 25B (a substantially rectangular space in a side view) (in the left-right direction, respectively). ), The first slide valve element 15A and the second slide valve element 15B of the main valve element 15 are slightly slidable in the left-right direction and substantially prevented from moving in the front-rear direction. The connection member 25 is fitted (particularly, see FIG. 7).

  The main valve body 15 fitted and supported by (the pair of connecting plates 25A, 25B) of the connecting body 25 is connected to the connecting plate 25A of the connecting body 25 by the reciprocating movement of the first and second pistons 21,22. , 25B (in this case, the first sliding valve body 15A of the main valve body 15 and the second sliding valve body 15A of the main valve body 15). The upper and lower surfaces of the slide valve body 15B are pressed so as to move between a cooling position (upper end position) and a heating position (lower end position).

  In this example, the case where the connecting body 25 is constituted by a pair of plate members (connection plates 25A and 25B) having the same size and the same shape is illustrated. Of course.

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

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

  Thus, 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. Are communicated with each other (via the main valve chamber 12), so that a cooling operation is performed in the heat pump cooling and heating system.

  When the main valve element 15 is in the cooling position (upper end position) (first communication state as shown in FIG. 1), the first working chamber 31 is connected to the discharge-side high-pressure port via a four-way pilot valve 90 described later. When the second working chamber 32 is connected to a port pD which is a suction-side low-pressure port while communicating with a certain port pA, high-pressure refrigerant is introduced into the first working chamber 31 and high-pressure refrigerant is supplied from the second working chamber 32. Refrigerant is discharged. Therefore, the pressure in the first working chamber 31 at one end (upper end) of the main valve chamber 12 becomes higher than the pressure in the second working chamber 32 at the other end (lower end) of the main valve chamber 12, as shown in FIG. As shown, the first and second pistons 21 and 22 and the main valve body 15 move downward, and the stopper 25s of the connecting body 25 (the supporting plate 25c of each of the connecting plates 25A and 25B) is moved to the lower connecting lid. 11e, the main valve body 15 is in the heating position (lower end position) (the 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. Are communicated with each other (via the main valve chamber 12), so that a heating operation is performed in the heat pump type cooling and heating system.

[Configuration of Four-Way Pilot Valve 90]
The four-way pilot valve 90 as a pilot valve has a well-known structure itself. As shown in an enlarged view in FIGS. 8A and 8B, an electromagnetic valve is provided on an outer periphery of a base end side (left end side). A coil case 91 is provided with a valve case 92 formed of a cylindrical straight pipe to which a coil 91 is fitted. Are located.

  The left end of the valve case 92 is hermetically joined by welding or the like to a flange portion (outer peripheral step portion) of the suction element 95. The suction element 95 is attached to a cover case 91A that covers the outer circumference of the electromagnetic coil 91 for energizing and energizing. It is fastened and fixed by bolts 92B.

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

  Further, a valve seat 93 having a flat inner end surface formed between the plunger 97 and the lid member 98 in the valve case 92 is hermetically joined by brazing or the like. The port b, which is connected to the first working chamber 31 of the above-described six-way valve body 10 via the thin tube #b in order from the front end side (right end side), and the port (intake side low pressure) The port c connected to the port pD via the thin tube #c, and the port d connected to the second working chamber 32 via the thin tube #d have a predetermined interval along the longitudinal direction (left-right direction) of the valve case 92. They are open side by side.

  The plunger 97 opposed to the suction element 95 is basically cylindrical, and is slidably disposed in the valve case 92 in the axial 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 for holding the valve body 94 slidably in the thickness direction at its free end side has its base end together with the fixture 94B. It is attached and fixed by press fitting, caulking, or the like. A leaf spring 94C for urging the valve body 94 in a direction (thickness direction) of pressing the valve body 94 against the valve seat 93 is attached to the valve body holder 94A. The valve body 94 is brought into contact with the valve seat surface of the valve seat 93 so as to switch the communication state between the ports b, c, and d that open to the valve seat surface of the valve seat 93. The valve seat slides along with the movement of the plunger 97 in the left-right direction.

  Further, the valve element 94 has such a size that it can selectively communicate between the adjacent ports bc and cd between the three ports b to d opening on the valve seat surface of the valve seat 93. A concave portion 94a is provided.

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

  The four-way pilot valve 90 is attached to an appropriate location such as the rear side of the six-way valve main body 10 via a fixture 92A. Further, in the four-way pilot valve 90, the thin tube #c is connected to the port pD which is the suction side low pressure port, 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 configured as described above, when the power to the electromagnetic coil 91 is turned off, the plunger 97 is actuated by the urging force of the compression coil spring 96 as shown in FIGS. The right end is pushed and moved to a position where it contacts the valve seat 93. In this state, the valve element 94 is located on the port b and the port c, and the port b and the port c communicate with each other through the concave portion 94a, and the port d and the valve chamber 99 communicate with each other. ) The high-pressure fluid flowing into the pA is introduced into the second working chamber 32 via the high-pressure capillary # a → the valve chamber 99 → port d → the capillary # d → port p12, and the high-pressure fluid in the first working chamber 31 is supplied to the port. It flows from p11 → capillary tube # b → port b → recess 94a → port c → capillary tube # c → port (suction side low pressure port) pD and is discharged.

  On the other hand, when the energization of the electromagnetic coil 91 is turned on, the plunger 97 is moved to a position where its left end contacts the suction element 95 by the suction force of the suction element 95 as shown in FIGS. (Against the biasing force of the compression coil spring 96). At this time, the valve body 94 is located above the port c and the port d, and the port c and the port d communicate with each other through the concave portion 94a, and the port b and the valve chamber 99 communicate with each other. The high-pressure fluid flowing into the pA is introduced into the first working chamber 31 through the high-pressure capillary # a → the valve chamber 99 → port b → the capillary # b → port p11, and the high-pressure fluid in the second working chamber 32 is supplied to the port p12. → The thin tube # d → the port d → the concave portion 94a → the port c → the thin tube # c → the port (low-pressure port on the suction side) pD.

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

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

[Operation 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 element (high pressure) when viewed in the left-right direction (the direction perpendicular to the axis O). The outer shape of the pressure receiving surface (pressure receiving area Sc) on the second slide valve element (low pressure side slide valve element) 15B side (back pressure side) in the side slide valve element 15A is a pair of the annular seal surface 15s in the first slide valve element 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 above-described conventional flow path switching valve. Since the pressure distribution on the surface 15s) is substantially uniform, good sealing performance, operability and stability can be ensured, and valve leakage can be effectively suppressed.

(Another example of the first embodiment)
In the first embodiment, in the width direction of the main valve body 15 (the front-rear direction in the illustrated example, 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 substantially equal to the outer shape of the contact area Sb of the annular seal surface 15s on the left side (specifically, slightly smaller than that). However, in order to further improve the sealing performance and stability, for example, as shown in FIGS. 9 to 11, the width dimension of the main valve body 15 is increased, and the first slide valve body is increased. 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.

(2nd Embodiment)
12 to 15 show a second embodiment of the flow path switching valve (six-way switching valve) according to the present invention.

  The passage switching valve 2 of the illustrated second embodiment is substantially the same as the passage switching valve 1 of the first embodiment except for the main valve body. Therefore, the portions corresponding to the respective portions of the flow path switching valve 1 of the first embodiment and the portions having the same functions are denoted by the same reference numerals, and the description thereof will not be repeated. In the following, differences around the main valve body will be described. The explanation will focus on the points.

  In the flow path switching valve 2 of the illustrated embodiment, the annular seal surface 15s provided on the left side (the 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. (Approximately the same width over the entire circumference).

  Also in this embodiment, when viewed in the left-right direction (the direction perpendicular to the axis O), 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 the left side. Of the contact area Sb of the annular seal surface 15s (all the circumference).

  In the flow path switching valve (six-way switching valve) 2 of the second embodiment, by adopting the above configuration, the same operation and effect as those of the flow path switching valve 1 of the first embodiment can be obtained. The contact area between the first sliding valve element 15A (the annular sealing surface 15s) and the first main valve seat 13 (the valve seat surface) is reduced, and the first contact with the first main valve seat 13 (the valve seat surface) is reduced. The pressing force (surface pressure) of (the annular sealing surface 15s) of the slide valve body 15A is increased, and the sealing performance can be further improved. In addition, the pressure receiving area Sc on the right side of the first slide valve body 15A can be reduced, so that the size can be reduced and the degree of freedom in arranging other assembly 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 passage switching valve 3 of the third embodiment is substantially the same as the passage switching valve 2 of the second embodiment except for the main valve body. Therefore, the portions corresponding to the respective portions of the flow path switching valve 2 of the second embodiment and the portions having the same function are denoted by the same reference numerals, and the description thereof will not be repeated. In the following, differences around the main valve body will be described. The explanation will focus on the points.

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

  Also in this embodiment, when viewed in the left-right direction (the direction perpendicular to the axis O), 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 the left side. 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 side.

  For example, in the flow path switching valve 2 of the second embodiment described above, by reducing the area of the annular seal surface 15s of the first slide valve element 15A, the first slide valve element 15A is used for switching the flow path. When sliding on the valve seat surface of the seat 13, the annular sealing surface 15 s of the first slide valve body 15 </ b> A is easily caught by the port opened in 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, the same operation and effect as those of the flow path switching valve 2 of the second embodiment can be obtained. The substantially bar-shaped convex 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 climb over the port opened in the valve seat surface of the first main valve seat 13, It is possible to effectively prevent the annular seal surface 15s of the first slide valve body 15A from being caught on the port.

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

  The passage switching valve 4 of the fourth embodiment is substantially the same as the passage switching valve 3 of the third embodiment except for the main valve body. Therefore, the portions corresponding to the respective portions of the flow path switching valve 3 of the third embodiment and the portions having the same functions are denoted by the same reference numerals, and redundant description is omitted. In the following, differences around the main valve body will be described. The explanation will focus on the points.

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

  For example, in the flow path switching valve 3 of the third embodiment described above, an O-ring as a seal member disposed between the first slide valve body 15A and the second slide valve body 15B (sliding surface gap). 18 becomes irregular and the difficulty of mold design and assembly work increases. Further, the tip portion of the bar-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, the same operation and effect as those of the flow path switching valve 3 of the third embodiment can be obtained. The shape of the O-ring 18 disposed between the first slide valve body 15A and the second slide valve body 15B (sliding surface gap) can be simplified, and the annular seal surface 15s and the convex portion having pressure distribution can be simplified. Since the root portion of the 15t is effectively pressed against the valve seat surface of the first main valve seat 13, the sealing performance 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 using the four-way pilot valve 90 has been described. The main valve body 15 may be driven in the main valve chamber 12 using the above.

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

  In addition, the flow path switching valves 1 to 4 of the present embodiment can be incorporated not only in a heat pump type cooling and heating 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) (fourth embodiment)
10 Six-way valve main body 11 Main valve housing 11A Upper lid member 11B Lower lid member 11a First piston portion 11b Second piston portion 11c Body 12 Main valve chamber 13 First main valve seat (valve seat)
14 2nd main valve seat (valve seat)
15 Main valve element 15A First slide valve element (high pressure side slide valve element)
15B 2nd slide valve body (low pressure side slide valve body)
15a Inner flange 15b of first slide valve element 15b Fitting convex part of second slide valve element 15s Annular sealing surface 15t of first slide valve element (high pressure side slide valve element) Convex part 16A First U-turn passage (high pressure side) U-turn passage)
16B 2nd U-turn passage (low-pressure side U-turn passage)
18 O-ring (annular sealing member)
21 First piston 22 Second piston 25 Connecting body 25A, 25B A pair of connecting plates 31 First working chamber 32 Second working chamber 90 Four-way pilot valve pA, pB, pC, pD, pE, pF Port

Claims (8)

A main valve housing defining a main valve chamber;
A first main valve seat disposed in the main valve chamber and having a valve seat surface on which a plurality of ports are opened;
A second main valve seat disposed in the main valve chamber on the opposite side of the first main valve seat with respect to an axis of the main valve chamber, and having a valve seat surface with a plurality of ports opened;
A high-pressure side slide valve element having a high-pressure side U-turn passage through 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 is introduced. And a pair of low-pressure side slide valve bodies that are slidable on the valve seat surface of the second main valve seat and have a low-pressure side U-turn passage. A main valve body arranged movably in the axial direction,
The pair of slide valve bodies are integrally movable in the axial direction, and are slidable with each other in a direction perpendicular to the axis.
By moving the main valve body in the main valve chamber, a flow path switching valve configured to switch communication between each of the plurality of ports of the first main valve seat and the second main valve seat. So,
The pair of slide valve bodies are formed around an opening of the high-pressure side U-turn passage in the high-pressure side slide valve body, and an annular seal surface that is in contact with the valve seat surface is formed.
A flow path, wherein an outer shape of a 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 an 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 convex portion having the same height as the annular sealing surface and having a width smaller than that of the annular sealing surface is continuously provided at the axial end portion of the annular sealing surface. Flow path switching valve.   4. The view according to claim 3, wherein when viewed in a direction perpendicular to the axis, the entirety of the convex surface portion is provided so as to be located inside a pressure receiving surface on the low pressure side slide valve body side. 5. Flow path switching valve.   When viewed in a direction perpendicular to the axis, a root portion of the convex portion is located inside a pressure-receiving surface on the low-pressure side slide valve body side, and a distal end portion of the convex portion is located 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.   The flow path switching valve according to any one of claims 3 to 5, wherein the convex portion is provided at least at a central portion in a width direction of the annular sealing surface.   An annular seal member is disposed between the high-pressure side slide valve element and the low-pressure side slide valve element, and an outer shape of the seal member is set larger than an outer shape of the annular seal surface. The flow path switching valve according to claim 1.   The high-pressure side slide valve element has a cylindrical shape, and a fitting projection that is slidably fitted inside the high-pressure side slide valve element is provided on one side surface of the low-pressure side slide valve element. The high-pressure side U-turn passage is defined by an inner peripheral surface of the high-pressure side slide valve body and an end face of the high-pressure side slide valve body by the fitting protrusion being internally fitted to the side slide valve body. The high-pressure side slide valve element and the low-pressure side slide valve element are integrally movable in the axial direction and slidable with each other in a direction perpendicular to the axis line. The flow path switching valve according to any one of claims 1 to 7, wherein the low pressure side U-turn passage is opened on the other side surface of the valve element.

Images