JP2019065895A - Six-way changeover valve - Google Patents

Abstract

To provide a six-way changeover valve capable of making valve leakage hard to occur and effectively suppressing a pressure loss.SOLUTION: A first U-turn passage 16A and a second U-turn passage 16B are provided inside of a main valve element 15. The main valve element is moved inside of a main valve chamber 12, thereby selectively taking: a first communication state where a port pA and a port pB are communicated via the first U-turn passage, a port pC and a port pD are communicated via the second U-turn passage and a port pE and a port pF are communicated via the inside of a main valve housing 11; and a second communication state where the port pA and the port pF are communicated via the first U-turn passage, the port pE and the port pD are communicated via the second U-turn passage, and the port pC and the port pB are communicated via the inside of the main valve housing.SELECTED DRAWING: Figure 1

Description

  The present invention relates to a six-way switching valve that switches flow paths by moving a valve body, and in particular, a six-way switching valve suitable for use as a flow path switching valve that switches flow paths in a heat pump type air conditioning system. About.

  In general, heat pump type air conditioning systems such as room air conditioners and car air conditioners, in addition to compressors, outdoor heat exchangers, indoor heat exchangers, expansion valves, etc., flow path switching valves as flow path (flow direction) switching means Is equipped.

  Although a four-way switching valve is well known as a flow channel switching valve of this type, it is considered to use a six-way switching valve instead.

  An example of the heat pump type | mold air conditioning system provided with the six-way switching valve below is easily demonstrated, referring FIG. 9 (A) and (B). The heat pump type air conditioning system 100 in the illustrated example switches the operation mode (cooling operation and heating operation) by the six-way switching valve 180, and basically, the compressor 110, the outdoor heat exchanger 120, and the indoor A six-way switching valve 180 having six ports pA, pB, pC, pD, pE, pF is disposed among them, provided with a heat exchanger 130, a cooling expansion valve 150, and a heating expansion valve 160. There is.

  The respective devices are connected by a flow path formed by a conduit or the like, and when the cooling operation mode is selected, as shown in FIG. 9A, the high temperature discharged from the compressor 110 The high-pressure refrigerant is led from the port pA of the six-way switching valve 180 to the outdoor heat exchanger 120 via the port pB, where it exchanges heat with outdoor air and condenses to form high-pressure gas-liquid two-phase or liquid refrigerant Then, it is introduced into the cooling expansion valve 150. The refrigerant of high pressure is decompressed by the cooling expansion valve 150, and the decompressed low pressure refrigerant is introduced from the port pE of the six-way switching valve 180 to the indoor heat exchanger 130 via the port pF. The refrigerant is exchanged (cooling) and evaporated, and the low temperature low pressure refrigerant is returned from the indoor heat exchanger 130 from the port pC of the six-way switching valve 180 to the suction side of the compressor 110 via the port pD.

  On the other hand, when the heating operation mode is selected, as shown in FIG. 9B, the high temperature / high pressure refrigerant discharged from the compressor 110 is sent from the port pA of the six-way switching valve 180 to the indoor through the port pF. It is led to the heat exchanger 130, where it exchanges heat with the room air (heating), condenses, and is introduced into the heating expansion valve 160 as a high pressure gas-liquid two-phase or liquid refrigerant. The high pressure refrigerant is decompressed by the heating expansion valve 160, and the low pressure refrigerant decompressed is introduced from the port pC of the six-way switching valve 180 through the port pB into the outdoor heat exchanger 120, where the outdoor air and the heat are reduced. The refrigerant is replaced and evaporated, and the low temperature and low pressure refrigerant is returned from the outdoor heat exchanger 120 from the port pE of the six-way switching valve 180 to the suction side of the compressor 110 through the port pD.

  As a six-way switching valve incorporated in a heat pump type cooling and heating system as described above, a sliding type as described in Patent Document 1 is known. This sliding six-way switching valve has a valve main body (main valve housing) incorporating a sliding main valve body and an electromagnetic pilot valve (four-way pilot valve), and the main valve housing includes the ports pA to pF. The slide main valve body is disposed slidably in the lateral direction. On the left and right sides of the sliding main valve body in the main valve housing, a pair of left and right piston type packings respectively connected to the sliding main valve body and connected to the compressor discharge side and the compressor suction side via pilot valves Two defined working chambers are provided, and introduction and discharge of high pressure fluid (refrigerant) to and from the two working chambers are selectively performed by the pilot valve, and the pressure difference between the two working chambers is used. The flow path switching is performed by sliding the slide type main valve body in the left and right direction.

JP-A-8-170864

  In the conventional flow path switching valve as described above, there are problems to be solved as follows.

  That is, in the slide type six-way switching valve described in Patent Document 1, five ports pB to pF of the six ports pA to pF are provided in line in the axial direction, and the five ports pA to pF are provided. The main valve seat on which the ports pB to pF are provided and the slide-type main valve body are elongated (in the axial direction), and the valve seat surface of the main valve seat on which the slide-type main valve body is slidably brought into contact It is difficult to ensure the surface accuracy (flatness) of the sealing surface of the valve body, and there is a possibility that leaks (valve leaks) due to initial leaks and durability deterioration may increase.

  Further, the high pressure fluid (refrigerant) collides with the inner wall surface and the like in the main valve housing having a relatively small internal volume, and the flow direction largely changes in a crank shape, so the pressure loss tends to be large.

  In addition to the above, in the conventional flow path switching valve, in particular, the flow path switching valve used in the above-described heat pump type cooling and heating system, high temperature and high pressure refrigerant (port pA to port pB, port pA to port) in the main valve housing The refrigerant flowing to pF) and the low-temperature low-pressure refrigerant (the refrigerant flowing from the port pC to the port pD, and the refrigerant flowing from the port pE to the port pD) flow in a close state. Specifically, the high-temperature high-pressure refrigerant and the low-temperature low-pressure refrigerant flow to the adjacent port pB and port pC via the main valve seat during cooling operation, and to the adjacent port pF via the main valve seat during heating operation Since the main valve seat, which is flowed to the port pC, and on which the respective ports are provided, is generally made of a metal having a high thermal conductivity, the amount of heat exchange (that is, heat loss) between them becomes large. There is also a problem that the system becomes inefficient.

  The present invention has been made in view of the above circumstances, and an object of the present invention is to provide a six-way switching valve which can suppress valve leakage and can effectively suppress pressure loss.

  Another object of the present invention is to provide a heat pump type air conditioning system capable of reducing heat loss when used in an environment where high temperature and high pressure fluid and low temperature and low pressure fluid flow such as a heat pump type air conditioning system. It is an object of the present invention to provide a six-way switching valve capable of improving the efficiency of

  In order to achieve the above object, a six-way switching valve according to the present invention basically comprises a cylindrical main valve housing defining a main valve chamber, and a total of six ports provided on the main valve housing, And a slide-type main valve body axially movably disposed in the main valve chamber, and a plurality of communication paths for selectively communicating between the ports are provided in the main valve body. By moving the main valve body, it is possible to switch between communicating ports, and in the main valve chamber, three ports are opened in line in the axial direction, and axes of the three ports are opened. On the opposite side, three other ports are opened side by side in the axial direction, and the main valve body is slidable in a cylindrical high pressure side slide valve body and the high pressure side slide valve body. A low pressure side slide valve body having a fitting convex portion to be internally fitted on one side Of the three ports by the inner peripheral surface of the high-pressure side slide valve body and the end face of the fitting convex portion by the high-pressure side slide valve body being internally fitted with the fitting convex portion. And a high pressure side U-turn passage into which a relatively high pressure fluid is introduced, and the high pressure side slide valve body and the low pressure side slide valve body extend in the axial direction. And can be mutually slidable in a direction perpendicular to the axis, and at the other side of the low-pressure slide valve, two of the other three ports. And the low pressure side U-turn passage into which a relatively low pressure fluid is introduced is opened, and the three ports are moved by moving the main valve body in the main valve chamber. Two ports of the high-pressure side U-turn In communication via a channel, two ports of the other three ports are in communication via the low pressure U-turn passage, and one other port of the three ports And the other one of the other three ports may be selectively connected in communication through the main valve housing.

  In a preferred aspect, an annular seal member is disposed between the high pressure side slide valve body and the fitting convex portion of the low pressure side slide valve body.

  In a further preferred aspect, the outer shape of the annular seal surface of the high pressure side slide valve body on the main valve seat side provided with the three ports is smaller than the outer shape of the seal member.

  In a further preferable aspect, an inner flange portion is provided on an inner periphery of an end portion on the main valve seat side provided with the three ports in the high pressure side slide valve body, and an end surface on the main valve seat side of the inner flange portion The annular sealing surface is formed on the

  In another preferable aspect, a biasing member that biases the high-pressure side slide valve body and the low-pressure side slide valve body in a direction opposite to each other between the high-pressure side slide valve body and the low-pressure side slide valve body. Are distributed.

  In a further preferred aspect, the biasing member is disposed outside the seal member.

  In another preferred embodiment, the passage area of the low pressure side U-turn passage is larger than the passage area of the high pressure side U-turn passage.

  In another preferred embodiment, the end face of the fitting convex portion is formed with a guide surface formed of a bowl-like depression that facilitates the flow of high-pressure fluid in the high-pressure side U-turn passage.

  In another preferable aspect, a volume defined by a pair of first and second pistons at one end and the other end of the main valve chamber in the main valve housing is a volume to which high pressure fluid is selectively introduced and discharged. Variable first and second working chambers are provided, and the main valve body is axially movably disposed interlocking with the first and second pistons, and the first and second working chambers are provided. By controlling the introduction and discharge of high pressure fluid to and from the main valve chamber, the first and second pistons are moved to move the main valve body in the main valve chamber.

  In a further preferable aspect, the first piston and the second piston are connected by one or a plurality of plate members disposed in a direction orthogonal to the valve seat surface of the main valve seat provided with the port. Integrally movably connected by the body, the main valve body is moved along with the reciprocating movement of the first and second pistons to the coupling body, and with respect to the valve seat surface of the main valve seat It is supported slidably in orthogonal directions.

  In a further preferred aspect, the coupling body is provided with a stopper portion for restricting the movement of the main valve body in the axial direction.

  In a further preferred aspect, the stopper portion is made to abut on the main valve housing.

  In the six-way switching valve according to the present invention, three ports are opened in the main valve chamber side by side in the axial direction, and another three ports are provided on the opposite side to the axes of the three ports. Aside from the high pressure U-turn passage, which is opened side by side in the axial direction and which selectively communicates two of the three ports into the main valve body and into which a relatively high pressure fluid is introduced. A low pressure side U-turn passage is provided to selectively communicate two of the three ports and to which a relatively low pressure fluid is introduced, and by moving the main valve body in the main valve chamber , Two of the three ports are in communication via the high pressure U-turn passage and two of the other three ports are in communication via the low pressure U-turn passage , One other port out of three ports Three other one port of the port is to obtain a communication state is caused to communicate (flow path) selectively plurality taken through the main valve housing. Therefore, since the main valve seat and main valve body in which the port is provided can be shortened (in the axial direction) as compared with the six-way switching valve using the conventional slide type main valve body, the valve seat surface of the main valve seat and the main valve The surface accuracy (flatness) of the sealing surface of the body can be easily secured, valve leakage can be suppressed, and fluid (for example, high-pressure fluid (refrigerant)) flows through the U-turn passage, thereby reducing pressure loss. You can also.

  In addition to the above, when the six-way switching valve according to the present invention is used in an environment where a high temperature / high pressure refrigerant and a low temperature / low pressure refrigerant flow, such as a heat pump type cooling / heating system, the high pressure side U-turn passage through which the high temperature / high pressure refrigerant flows Since the low pressure side U-turn passage through which the low temperature and low pressure refrigerant flows is provided relatively widely apart without, for example, via the metal main valve seat, the high temperature and high pressure refrigerant and the low temperature and low pressure refrigerant are metal. Compared with the conventional one that is flowed in close proximity via the main valve seat, the amount of heat exchange (that is, heat loss) between them can be significantly reduced, and thus the effect of improving the efficiency of the system is also obtained. Be

  Further, in the six-way switching valve according to the present invention, the main valve body has a cylindrical high-pressure side slide valve body and a fitting convex portion slidably fitted in the high-pressure side slide valve body. And the low pressure side slide valve body having the side surface on the side slide valve body side, and the inner surface of the high pressure side slide valve body and the engagement convex by fitting the fitting convex portion to the high pressure side slide valve body. The high pressure side U-turn passage is defined by the end face of the part, so that the main valve seat where the low pressure side slide valve body is provided with a port by the high pressure fluid introduced in the high pressure side U turn passage It is pressed (pressed). Therefore, valve leakage can be more effectively suppressed while suppressing the size of the main valve body (in particular, the size in the direction orthogonal to the axis).

  Further, the outer shape of the annular seal surface of the high pressure side slide valve body on the main valve seat side provided with the three ports is disposed between the high pressure side slide valve body and the fitting convex portion of the low pressure side slide valve body. The main valve in which the high pressure side slide valve body is provided with a port by the differential pressure acting on the high pressure side slide valve body due to the difference in pressure receiving area of the high pressure side slide valve body. Since it is pressed against the seat (pressure contact), this also makes it possible to more effectively suppress valve leakage.

  The subject, composition, and an effect other than the above-mentioned are clarified by the following embodiments.

The longitudinal cross-sectional view which shows the 1st communication state (during cooling operation) of one Embodiment of the six-way switching valve concerning this invention. The longitudinal cross-sectional view which shows the 2nd communication state (at the time of heating operation) of one Embodiment of the six-way switching valve which concerns on this invention. The principal part expansion longitudinal cross-sectional view which expands and shows the principal part of the six-way switching valve shown by FIG. FIG. 2 is a cross-sectional view taken along the line U-U in FIG. The perspective view which shows the main valve body and connection body of one Embodiment of the six-way switching valve which concerns on this invention. It is a figure which expands and shows the four-way pilot valve used for the six-way switching valve based on this invention, (A) is a 1st communication state (at the time of air conditioning operation) (at the time of electricity supply OFF), (B) is a 2nd communication state. The longitudinal cross-sectional view which respectively shows (at the time of heating operation) (at the time of electricity supply ON). The principal part expansion longitudinal cross-sectional view which expands and shows the principal part of other examples of the six-way switching valve shown by FIG. The principal part expansion longitudinal cross-sectional view which expands and shows the principal part of the further another example of the six-way switching valve shown by FIG. BRIEF DESCRIPTION OF THE DRAWINGS In an example of the heat pump type | mold air conditioning system in which the six-way switching valve was used as a flow-path switching valve, (A) is a schematic block diagram respectively showing at the time of air conditioning operation, (B) at the time of heating operation.

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

  1 and 2 are longitudinal sectional views showing an embodiment of a six-way switching valve according to the present invention, and FIG. 1 shows a first communication state (during cooling operation) and FIG. 2 shows a second communication state (heating During operation).

  In the present specification, descriptions representing positions, directions such as upper and lower, right and left, front and rear, etc. are provided for convenience according to the drawings to avoid complicated explanation, and are actually incorporated into a heat pump type air conditioning system etc. It does not necessarily indicate the position or direction in the closed state.

  Further, in each drawing, the gap formed between the members, the separation distance between the members, and the like are large in comparison with the dimensions of the respective constituent members in order to facilitate understanding of the invention and for convenience in drawing. Or it may be drawn small.

  The six-way switching valve 1 of the illustrated embodiment is, for example, a slide type used as the six-way switching valve 180 in the heat pump type cooling and heating system shown in FIGS. 9 (A) and 9 (B) described above. A six-way valve body 10 and a single electromagnetic four-way pilot valve 90 as a pilot valve are provided. The six ports provided in the six-way switching valve 1 of the present embodiment are assigned the same reference numerals in correspondence with the ports pA to pF of the six-way switching valve 180.

[Configuration of six-way valve main 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 first working chamber 31, the first operating chamber 31, the One piston 21, a main valve chamber 12, a second piston 22, and a second working chamber 32 are disposed. In each of the first and second pistons 21 and 22, a spring-loaded packing whose outer peripheral portion is in pressure contact with the inner peripheral surface of the main valve housing 11 is attached 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 disc-like upper connecting lid 11d airtightly attached to the upper end opening portion 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 disposed in the first piston portion 11a. Similarly, in a central hole provided in a thick disk-shaped lower connection lid 11e airtightly attached to the lower end opening of the body portion 11c, a second piston portion formed of a pipe member (having a relatively small diameter) 11b is airtightly fixed by brazing or the like, and the second piston 22 is disposed in the second piston portion 11b.

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

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

  More specifically, a first main valve seat (valve sheet) 13 made of, for example, a metal whose surface (right surface) is flat at the center of the left portion of the main valve chamber 12 is a main valve by brazing or the like. Three ports consisting of a pipe joint that is airtightly fixed to (the inner circumference of) the body portion 11c of the housing 11 and extends to the left on the valve seat surface of the first main valve seat 13 (in order from the upper end side The ports pB, the ports pA, and the ports pF) are opened at substantially equal intervals (aligned in the direction of the axis O) in vertical alignment.

  In addition, the surface (left surface) of the right center of the main valve chamber 12 (a position facing the first main valve seat 13, in other words, a position opposite to the first main valve seat 13 with respect to the axis O) The second main valve seat (valve sheet) 14 made of metal, for example, having a flat valve seat surface is airtightly fixed to (the inner periphery of) the body portion 11c of the main valve housing 11 by brazing or the like. In the valve seat surface of the second main valve seat 14, three ports (a port pC, a port pD and a port pE) consisting of a pipe joint extending rightward are arranged longitudinally (in the direction of the axis O) They are opened at approximately equal intervals).

  Each port (port pB, port pA, port pF) provided in the first main valve seat 13 and each port (port pC, port pD, port pE) provided in the second main valve seat 14 face each other. It is set to the position (opposite side with respect to the axis O), and in the present 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 It is done.

  In the main valve chamber 12, specifically, in the body portion 11c of the main valve housing 11, both side surfaces (left and right surfaces) are the valve seat surfaces of the first main valve seat 13 and the second main valve seat 14. A slide-type main valve body 15 having a rectangular cross-sectional shape having a racetrack-shaped annular seal surface slidably brought into contact with each other is disposed movably 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 made 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, 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 side (right side) second slide valve body (low-pressure side slide valve body) 15B.

  The first slide valve body 15A has a tubular shape, and is open at the inner periphery of the left end portion (the end portion on the opposite side to the second slide valve body 15B side) to the valve seat surface of the first main valve seat 13 The inner flange portion 15a has an opening sized so as to allow the two adjacent ports (port pB and port pA, or port pA and port pF) of the ports to selectively communicate with each other. 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 seal surface slidably brought into contact with the valve seat surface of the first main valve seat 13 .

  On the other hand, on the right side (the side opposite to the first slide valve body 15A side) of the second slide valve body 15B, adjacent two of the three ports opened in the valve seat surface of the second main valve seat 14 Second U-turn passage (low-pressure side U-turn passage) (communication passage) consisting of a bowl-like depression sized to selectively communicate one port (port pC with port pD, or port pD with port pE) 16B is opened, and on the left surface (the side surface on the first slide valve body 15A side) of the second slide valve body 15B, the inner shape of the cylindrical first slide valve body 15A is substantially the same or slightly smaller than that A fitting convex portion 15b having an outer shape is extended (leftward).

  The fitting convex portion 15b of the second slide valve body 15B can slide on (the right side portion of) the cylindrical first slide valve body 15A (with the O-ring 18 interposed in the step portion provided therebetween) By being internally fitted, the adjacent one of the three ports opened on the valve seat surface of the first main valve seat 13 by the inner peripheral surface of the first slide valve body 15A and the left end surface of the fitting convex portion 15b. A first U-turn passage (high-pressure side U-turn passage) (communication passage) 16A capable of selectively communicating two matching ports (port pB and port pA, or port pA and port pF) is defined. The first slide valve body 15A and the second slide valve body 15B are in the left-right direction (a direction perpendicular to the axis O and each port provided on the first main valve seat 13 (port pB, port pA, port pF) and the second main valve seat 14 Slightly movable mutually in the direction in which the ports (port pC, port pD, port pE) face each other, that is, in the direction orthogonal to the valve seat surfaces of the first main valve seat 13 and the second main valve seat 14) And, it is integrally movable in the vertical direction (the direction of the axis O).

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

  Therefore, a high pressure fluid (refrigerant) is introduced from the port (discharge side high pressure port) pA through the first U-turn passage 16A to a portion inside the O-ring 18, and the first U-turn passage 16A and the main valve chamber 12 It is sealed (sealed) by the O-ring 18 disposed therebetween.

  Here, as is well understood by referring to FIG. 3 together with FIGS. 1 and 2, when viewed in the left-right direction (direction perpendicular to the axis O), the pressure receiving area Sb on the right side of the first slide valve body 15A is It is larger than the pressure receiving area Sa on the left side (the first main valve seat 13 side).

  More specifically, the projection area on the inner side of the O-ring 18 with respect to a plane perpendicular to the left and right direction, and the high pressure refrigerant introduced into the first U-turn passage 16A (the right side of the first slide valve body 15A) The projected area (pressure receiving area Sb) of the surface receiving pressure in the left direction is the projected area of the annular seal surface on the side of the first main valve seat 13 with respect to a plane perpendicular to the left and right direction The projected area (pressure receiving pressure) of the surface to which the first slide valve body 15A (the left face of the first slide valve body) receives pressure in the right direction by the high pressure refrigerant flowing through the port (the inner side of the annular seal surface) The area Sa) is made larger.

  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) received from (the high-pressure refrigerant of) the first U-turn passage 16A. 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 makes the right surface (annular seal 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 in pressure receiving area (Sb-Sa) between the right side and the left side of the first slide valve body 15A. The left pressure (the annular seal surface) 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 slide valve body 15A.

  In addition, between the first slide valve body 15A and the second slide valve body 15B, for example, on the outside of the O-ring 18, the fitting convex portion of the right surface of the first slide valve body 15A and the second slide valve body 15B. Biasing member (ring shape) for biasing the first slide valve body 15A and the second slide valve body 15B in opposite directions (in a direction away from each other) between the step surface (left facing terrace surface) forming the surface 15b Plate spring, a compression coil spring, etc.), thereby pressing (pressing) the left surface (an annular seal surface) of the first slide valve body 15A against the valve seat surface of the first main valve seat 13, The right side surface (the annular seal surface) of the two-slide valve body 15B may be brought into pressure contact with the valve seat surface of the second main valve seat 14.

  In the present embodiment, a reinforcement pin 15d for shape retention is installed in the front-rear direction substantially at the center of the second U-turn passage 16B of the second slide valve body 15B (see also FIG. 5).

  Further, in this example, support plate portions of (the connection plates 25A, 25B of) the connecting body 25 described later on the upper and lower surfaces of the main valve body 15 (the first slide valve body 15A and the second slide valve body 15B constituting the main valve body 15). A recessed surface 15e is formed in which the surface 25c is fitted (with a slight gap in the left-right direction).

  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 direction of the axis O, and as shown in FIG. The port pB is opened and the port pA is communicated with the port pA through the first U-turn passage 16A of the first slide valve body 15A, and the port pE is opened. The port pC and the port pD are turned second U-turn of the second slide valve body 15B. The cooling position (upper end position) communicated via the passage 16B, the port pB is opened and the port pA and the port pF are opened via the first U-turn passage 16A of the first slide valve body 15A as shown in FIG. The heating position (lower end position) in which the port pC is opened and the port pD is communicated with the port pE via the second U-turn passage 16B of the second slide valve body 15B while being communicated. ) It is a to obtain selective to take.

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

  The first piston 21 and the second piston 22 are connected by the connecting body 25 so as to be integrally movable, 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. In the left and right direction, the small amount of sliding and the movement in the back and forth direction are substantially prevented from being fitted and supported.

  In the present embodiment, the connecting body 25 is formed of, for example, a pair of plate members having the same size and the same shape, which are manufactured by, for example, press molding. The pair of plate members are disposed along (in other words, parallel to a plane orthogonal to the valve seat surface) along the direction orthogonal to the valve seat surface of the main valve seat 14, and the pair of plate members The main valve body 15 is interposed between the pair of plate members (in the front-rear direction). Hereinafter, the plate material disposed on the front side of the main valve body 15 is referred to as a connection plate 25A, and the plate material disposed on the rear side of the main valve body 15 is referred to as a connection plate 25B.

  More specifically, as best seen by reference to FIGS. 4 and 5 together with FIGS. 1 and 2, each connecting plate 25A, 25B is symmetrical with respect to a central line (symmetrical line) extending in the front-rear direction from the center thereof. It is comprised by the board | plate material of vertically long rectangular shape (here, the same width covering a vertical whole length). The main valve body 15 (the front side portion or the rear side portion) is movably supported integrally in the direction of the axis O at substantially the center (in the vertical direction) of the connection plates 25A, 25B. A support plate portion 25c having a shape (that is, a substantially concave shape in cross section) along the outer periphery (the front and upper and lower surfaces, or the rear and upper and lower surfaces) of the valve body 15 is formed. The width (in the left-right direction) of the support plate portion 25c is slightly smaller than the width of the recessed surface 15e provided on the upper and lower surfaces of the valve body 15.

  A connection plate 25a extending to the first piston 21 or the second piston 22 is connected to the upper and lower sides of the support plate 25c in each of the connection 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 of the connection plate 25A on the front side is opened on the valve seat surface of the first main valve seat 13 and the second main valve seat 14 as viewed from the front of the axis O, particularly in the left and right direction. It is disposed at a position avoiding the six ports pA to pF on the front side (in other words, a position offset to the front from the six ports pA to pF), and the offset of the connecting plate portion 25a in the rear connecting plate 25B. The plate portion 25aa has six ports pA to pF that are opened on the valve seat surfaces of the first main valve seat 13 and the second main valve seat 14 viewed from the axis O, especially 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 to 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 between offset plate portions 25aa of the connection plate portions 25a of the pair of connection plates 25A and 25B, which are spaced apart (in the front-rear direction) from the diameters of the ports pA to pF. More specifically, port pF and port pE located on the lower side in the cooling position (upper end position) shown in FIG. 1 and ports pB and pC located on the upper side in the heating position (lower end position) shown in FIG. It will be positioned (see especially FIG. 4).

  In addition, the contact plate portion 25ab of the connection plate portion 25a in the connection plates 25A and 25B (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 A portion not overlapping with each port pA to pF opened in the valve seat surface is brought into contact with the contact plate portion 25ab of the connection plate portion 25a in the opposite (opposedly disposed) connection plate 25B, 25A ing. Note that, in consideration of the assemblability and the like described later, for example, in order to mutually align the connection plates 25A and 25B disposed opposite to each other, the contact plate portion 25ab may be provided with asperities (alignment portions). .

  At the upper and lower ends of (the connection plate portions 25a of) the connection plates 25A, 25B, the opposite side to the connection plates 25B, 25A that are disposed opposite to each other (direction in which the support plate portions 25c having a substantially concave cross section) The mounting leg 25b is formed so as to be bent approximately 90 ° toward the end, and the bolt 30 connecting the connecting plates 25A and 25B to the first piston 21 or the second piston 22 is inserted through the mounting leg 25b. A threaded hole 29 is formed through it.

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

  In other words, in the present example, the upper connecting lid 11d or the lower connecting lid 11e of the main valve housing 11 abuts on (the support plates 25c of the respective connecting plates 25A, 25B of the connecting body 25). There is provided a stopper portion 25s for restricting the movement in the vertical direction.

  As described above, the upper end side lid member 11A and the lower end side lid member 11B are directed upward of the first piston 21 by providing the connecting member 25 with the stopper portion 25s for restricting the movement of the main valve body 15, for example. The load applied to the first and second pistons 21 and 22 can be reduced as compared with the one that also serves as a stopper that blocks the movement of the second piston 22 and the downward movement of the second piston 22. The dimensional accuracy of the components of the first and second pistons 21 and 22 and the upper and lower lids 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 in the upward direction of the first piston 21 and move in the downward direction of the second piston 22 (that is, the upper and lower sides of the main valve body 15). Of course, it may also serve as a stopper for preventing movement.

  In this example, as described above, since the connection plates 25A and 25B are formed of plate members having the same size and shape, the two connection plates 25A and 25B are disposed to face each other in the front-rear direction, and The contact plates 25 ab of the connection plates 25 a of the two connection plates 25 A, 25 B are arranged in contact in opposite directions (specifically, upside down) and arranged in combination, and each attachment is made via the bolt 30 The leg 25 b 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 (in the left-right direction, respectively) between the support plate portions 25c in the respective connection plates 25A, 25B (space in substantially rectangular shape in side view) From the above), with the first slide valve body 15A and the second slide valve body 15B of the main valve body 15 being slightly slidable in the left-right direction and substantially prevented from moving in the front-rear direction The connector 25 is fitted (especially, see FIG. 5).

  The main valve body 15 fitted and supported by (the pair of connecting plates 25A, 25B of) the connecting body 25 has the connecting plate 25A of the connecting body 25 as the first and second pistons 21 and 22 reciprocate. , 25B is pushed by the upper part or the lower part (a rectangular plane which is wide in the left-right direction) of the support plate part 25c having a concave cross section (here, the first slide valve body 15A of the main valve body 15 and the second 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 addition, although the case where the said connection body 25 is comprised by a pair of board | plate material (connection board 25A, 25B) of the same dimension and the same shape is illustrated in this example, for example, the connection body 25 is one board material. It is natural that you may constitute.

[Operation of six-way valve main body 10]
Next, the operation of the six-way valve main body 10 having the configuration as described above 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 fourth valve pilot circuit 90 described later When the second working chamber 32 is communicated with the port pA which is the discharge side high pressure port, and the first working chamber 31 is communicated with the port pD which is the suction side low pressure port, a high temperature and high pressure refrigerant is introduced into the second working chamber 32 The high temperature and high pressure refrigerant is discharged from the first working chamber 31. Therefore, the pressure in the second working chamber 32 on the other end side (lower end side) of the main valve chamber 12 becomes higher than the pressure in the first working chamber 31 on one end side (upper end side) of the main valve chamber 12. As the first and second pistons 21 and 22 and the main valve body 15 move upward, the stopper portions 25s of (the support plate portions 25c of the connecting plates 25A and 25B of) the connecting body 25 move upward. The main valve body 15 takes a cooling position (upper end position) (first communication state as shown in FIG. 1).

  Thereby, port pA and port pB are communicated (via first U-turn passage 16A), port pC and port pD are communicated (via second U-turn passage 16B), and port pE and port pF are communicated. As a result, the cooling operation is performed in the heat pump type cooling and heating system.

  When the main valve body 15 is in the cooling position (upper end position) (the first communication state as shown in FIG. 1), the first working chamber 31 is set to the discharge side high pressure port via the four way pilot valve 90 described later. When the second working chamber 32 is communicated with the port pD which is the suction side low pressure port while communicating with a certain port pA, the high temperature / high pressure refrigerant is introduced into the first working chamber 31 and the high temperature from the second working chamber 32 High pressure refrigerant is discharged. Therefore, the pressure in the first working chamber 31 at one end side (upper end side) of the main valve chamber 12 becomes higher than the pressure in the second working chamber 32 at the other end side (lower end side) of the main valve chamber 12, as shown in FIG. As the first and second pistons 21 and 22 and the main valve body 15 move downward, the stopper portions 25s of (the support plate portions 25c of the respective connection plates 25A and 25B of) the connection body 25 move downward. The main valve body 15 is brought into a heating position (lower end position) (a second communication state as shown in FIG. 2).

  Thereby, port pA and port pF are communicated (via first U-turn passage 16A), port pE and port pD are communicated (via second U-turn passage 16B), and port pC and port pB are communicated. As a result, the heating operation is performed in the heat pump type cooling and heating system, because

[Configuration 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. It has a valve case 92 consisting of a cylindrical straight pipe on which a coil 91 is externally fixed and fixed, and a suction element 95, a compression coil spring 96 and a plunger 97 are arranged in series in this valve case 92 from the base end side. It is present.

  The left end portion of the valve case 92 is sealingly joined to the hook-like portion (outer periphery stepped portion) of the suction element 95 by welding or the like, and the suction element 95 is attached to the cover case 91A covering the outer periphery of the electromagnetic coil 91 for energization excitation. It is fastened and fixed by a bolt 92B.

  On the other hand, at the right end opening of the valve case 92, a filter-attached lid member 98 having a thin tube insertion port (high pressure introduction port a) for introducing high pressure refrigerant is airtightly attached by welding, brazing, caulking or the like. The region enclosed by the lid member 98, the plunger 97 and the valve case 92 is a valve chamber 99. From the port (discharge side high pressure port) pA via a flexible high pressure thin tube #a airtightly inserted into the thin tube insertion port (high pressure introduction port a) of the lid member 98 in the valve chamber 99 A high temperature and high pressure refrigerant is introduced.

  Further, a valve seat 93 whose inner end face is a flat valve seat surface is airtightly joined between the plunger 97 and the lid member 98 in the valve case 92 by brazing or the like. Port b connected to the first working chamber 31 of the six-way valve main body 10 via the thin tube #b sequentially from the tip end side (right end side) on the valve seat surface (inner end face) of Port c connected to pD via capillary #c and port d connected to second working chamber 32 via capillary #d have a predetermined interval along the longitudinal direction (left-right direction) of valve case 92 They are opened side by side.

  The plunger 97 disposed opposite to the suction element 95 basically has a cylindrical shape, and is slidably disposed in the valve case 92 axially (in a direction along the center line L of the valve case 92). . At the end of the plunger 97 on the opposite side to the suction element 95 side, a valve body holder 94A for holding the valve body 94 slidably in the thickness direction at the free end side thereof has its base end together with the attachment 94B. It is fixed by press fitting, caulking, etc. A leaf spring 94C is attached to the valve body holder 94A to bias the valve body 94 in the direction (thickness direction) of pressing the valve seat 93. The valve body 94 is in contact with the valve seat surface of the valve seat 93 so as to switch the communication state between the ports b, c, d opened in the valve seat surface of the valve seat 93. The valve seat surface is slid along with the movement of the plunger 97 in the left-right direction.

  Also, the valve body 94 is sized so as to selectively communicate between adjacent ports b-c and c-d of the three ports b-d opened in the valve seat surface of the valve seat 93. A recess 94a is provided.

  The compression coil spring 96 is compressed between the suction element 95 and the plunger 97 to bias the plunger 97 away from the suction element 95 (to the right in the figure). 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 this stopper.

  The four-way pilot valve 90 is attached to an appropriate place such as the back side of the six-way valve main body 10 through the attachment 92A. In the four-way pilot valve 90, the capillary #c is connected to the port pD which is the suction side low pressure port, but the capillary #c may be connected to the port pC where 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 electromagnetic coil 91 is deenergized, the plunger 97 is biased by the compression coil spring 96 as shown in FIGS. 1 and 6A. 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 recess 94a allows the port b and the port c to communicate with each other and the port d and the valve chamber 99 to communicate with each other. ) The high pressure fluid flowing into pA is introduced into the second working chamber 32 via the high pressure capillary #a → valve chamber 99 → port d → capillary #d → port p12, and the high pressure fluid in the first operation chamber 31 is port p11 → thin tube # b → port b → concave portion 94a → port c → thin tube # c → port (intake side low pressure port) pD and discharged.

  On the other hand, when the energization of the electromagnetic coil 91 is turned on, as shown in FIG. 2 and FIG. 6B, the plunger 97 is positioned such that its left end abuts on the aspirator 95 by the suction force of the aspirator 95. (Against the biasing 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 while the port c and the port d communicate with each other by the recess 94 a and the port b and the valve chamber 99 communicate, the port (discharge side high pressure port) The high pressure fluid flowing into pA is introduced into the first working chamber 31 via the high pressure capillary #a → valve chamber 99 → port b → capillary #b → port p11, and the high pressure fluid in the second operating chamber 32 is port p12. → The capillary #d → port d → the recess 94a → the port c → the capillary #c → the port (intake side low pressure port) pD and discharged.

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

  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 ON / OFF energization to the electromagnetic four-way pilot valve 90. By moving the main valve body 15 constituting the six-way valve main body 10 within the main valve chamber 12 using the differential pressure between the flowing fluid) and the low pressure fluid (fluid flowing through the port pD which is the low pressure portion) The state of communication between the six ports provided in total in the housing 11 is switched, and switching from heating operation to cooling operation and switching from cooling operation to heating operation can be performed in the heat pump type cooling and heating system.

[Operation effect of six-way switching valve 1]
As understood from the above description, in the six-way switching valve 1 of the present embodiment, the port pB, the port pA, and the port pF are opened in the direction of the axis O in the main valve chamber 12 in parallel. The port pC, the port pD, and the port pE are opened side by side in the direction of the axis O on the opposite side to the axis O of the port pA and the port pF, and the first U-turn passage 16A and the main valve body 15 are opened. A second U-turn passage 16B is provided, and by moving the main valve body 15 in the main valve chamber 12, the port pA and the port pB are communicated with each other through the first U-turn passage 16A, and the port pC and the port pD are The first communication state in which the port pE and the port pF are communicated via the main valve chamber 12 and the port pA and the port pF are communicated with each other through the second U-turn passage 16B. A second communication state in which 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 via the main valve chamber 12 are communicated via the 1U turn passage 16A. And are to be taken selectively. Therefore, the main valve seat (the first main valve seat 13 and the second main valve seat 14) and the main valve body 15 in which the ports are provided (the axis O Surface accuracy (flatness) of the valve seat surface of the main valve seat (the first main valve seat 13 and the second main valve seat 14) and the sealing surface of the main valve body 15 can be easily secured. Since the valve leakage can be suppressed and the fluid (for example, high pressure fluid (refrigerant)) is allowed to flow through the first U-turn passage 16A, pressure loss can also be reduced.

  Further, in the present embodiment, the fluid (for example, low pressure refrigerant) flowing in the six-way valve main body 10 flows through the second U-turn passage 16B, and the fluid (for example, medium pressure refrigerant) flows in the main valve chamber 12 in the left and right direction. As it is flowed (straight), this also makes it possible to reduce the pressure loss.

  In addition to the above, when using the six-way switching valve 1 according to the present invention in an environment where a high temperature / high pressure refrigerant and a low temperature / low pressure refrigerant flow, such as a heat pump type cooling / heating system, the first U-turn passage (High-pressure side U-turn passage) 16A and second U-turn passage (low-pressure side U-turn passage) 16B in which low temperature and low pressure refrigerant flows are provided relatively widely apart, for example, without metal main valve seat Compared to the conventional type in which the high-temperature high-pressure refrigerant and the low-temperature low-pressure refrigerant flow in close proximity via the metal main valve seat, the amount of heat exchange between them (that is, heat loss) It is possible to reduce the system efficiency, and thus to improve the system efficiency.

  Further, in the six-way switching valve 1 according to the present invention, the main valve body 15 is slidably fitted on the cylindrical first slide valve body (high pressure side slide valve body) 15A and the first slide valve body 15A. And the second slide valve body (low-pressure side slide valve body) 15B having the fitting projection 15b on the left side surface (side surface on the first slide valve body 15A side), and is fitted to the first slide valve body 15A The first U-turn passage (high-pressure side U-turn passage) 16A is defined by the inner peripheral surface of the first slide valve body 15A and the left end surface of the fitting convex portion 15b by internally fitting the convex portion 15b. Therefore, the second slide valve body 15B is pressed (pressure-contacted) to the second main valve seat 14 provided with the port by the high pressure fluid (fluid pressure) introduced into the first U-turn passage 16A. Therefore, it is possible to more effectively suppress the valve leakage while suppressing the size of the main valve body 15 (in particular, the size in the direction orthogonal to the axis O).

  Further, the outer shape of the annular seal surface of the first slide valve body 15A on the first main valve seat 13 side provided with three ports (port pB, port pA, and port pF) is the same as the first slide valve body 15A. Since the outer diameter of the O-ring 18 disposed between the second slide valve body 15B and the fitting convex portion 15b is smaller than the outer shape of the O ring 18, the first slide valve is caused due to the difference in pressure receiving area of the first slide valve body 15A. Since the first slide valve body 15A is pressed (pressed) against the first main valve seat 13 provided with the port by the differential pressure acting on the body 15A, this also makes it possible to suppress the valve leakage more effectively. .

[Another example of the six-way switching valve 1]
In the above embodiment, the passage area (cross-sectional area substantially perpendicular to the flow direction) of the second U-turn passage (low-pressure side U-turn passage) 16B on the second slide valve body 15B side and the first slide valve body 15A side Of the first U-turn passage (high-pressure side U-turn passage) 16A is approximately the same as the passage area (cross-sectional area substantially perpendicular to the flow direction), but the second U-turn passage (low-pressure side U-turn passage) 16B Is larger than that of the first U-turn passage (high-pressure side U-turn passage) 16A (in other words, the high-pressure refrigerant flowing through the first U-turn passage 16A is compressed), etc. The second slide valve body 15B (in the illustrated example, the fitting convex portion 15b) is enlarged, and the passage area of the second U-turn passage 16B is larger than the passage area of the first U-turn passage 16A. Weird It may be. According to this configuration, the high and low pressure channel ratio of the low pressure side U-turn passage and the high pressure side U-turn passage can be set optimally. For this reason, it is especially suitable as a flow passage switching valve used for an air conditioning system or the like in which the flow passage area of the low pressure side flow passage is larger than the flow passage area of the high pressure side flow passage.

  In the above embodiment, the first U-turn passage (high-pressure side U-turn passage) 16A on the first slide valve body 15A side is substantially concave, but the flow of high-pressure refrigerant in the first U-turn passage 16A is smoothened. In order to reduce noise, as shown in FIG. 8, a guide surface 15c is formed on the left end surface of the fitting convex portion 15b of the second slide valve body 15B, and the corner portion is a rounded depression. May be In this case, it is preferable that the left end surface of the fitting convex portion 15b of the second slide valve body 15B be disposed close to the inner flange portion 15a of the first slide valve body 15A as illustrated.

  In the six-way switching valve 1 of the above embodiment, the configuration for driving the main valve body 15 in the main valve chamber 12 using the four-way pilot valve 90 has been described, but using a motor instead of the four-way pilot valve 90, for example. The main valve body 15 may be driven in the main valve chamber 12.

  Moreover, it is needless to say that the six-way switching valve 1 of the present embodiment can be incorporated not only in the heat pump type cooling and heating system but also in other systems, devices, and devices.

1 six-way switching valve 10 six-way valve main body 11 main valve housing 11A upper end side lid member 11B lower end side lid member 11a first piston portion 11b second piston portion 11c body portion 12 main valve chamber 13 first main valve seat (valve seat)
14 2nd 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 1st U-turn passage (high-pressure side U-turn passage) (communication passage) 15a inner slide-like portion 15b of the first slide valve body fitting convex portion 15c of the second slide valve body guide surface 15e of the second slide valve body recessed surface 16A
16B 2nd U-turn passage (low pressure side U-turn passage) (communication passage)
18 O-ring (annular seal member)
21 first piston 22 second piston 25 coupling body 25A, 25B pair of connecting plates 25a connection plate portion 25aa offset plate portion 25ab contact plate portion 25b mounting leg portion 25c support plate portion 25s stopper portion 31 of first body of the coupling body 32 Second working chamber 90 Four-way pilot valve pA, pB, pC, pD, pE, pF port

Claims (12)

A cylindrical main valve housing defining a main valve chamber, a total of six ports provided on the main valve housing, and a slide-type main valve axially movably disposed in the main valve chamber A plurality of communication paths for selectively communicating between the ports are provided in the main valve body, and by moving the main valve body, it is possible to switch between the communicating ports It is a six-way switching valve,
In the main valve chamber, three ports are opened in line in the axial direction, and another three ports are opened in line in the axial direction on the opposite side to the axis of the three ports. ,
The main valve body has a cylindrical high-pressure side slide valve body and a low-pressure side slide valve body having on one side a fitting protrusion slidably fitted in the high-pressure side slide valve body, By fitting the fitting convex portion to the high pressure side slide valve body, two of the three ports are formed by the inner peripheral surface of the high pressure side slide valve body and the end face of the fitting convex portion. A high pressure side U-turn passage is defined to selectively communicate the individual ports and into which a relatively high pressure fluid is introduced, and the high pressure side slide valve body and the low pressure side slide valve body are integrally integrated in the axial direction Movable, and mutually slidable in a direction perpendicular to the axis, and at the other side of the low-pressure slide valve, two ports out of the other three ports Low pressure side U Down passage has been opened,
By moving the main valve body in the main valve chamber,
Two of the three ports are in communication via the high pressure U-turn passage, and two of the other three ports are via the low pressure U-turn passage. Select a communication state in which the other one of the three ports and the other one of the other three ports are communicated through the main valve housing. A six-way switching valve characterized in that a plurality of valves can be taken.   The six-way switching valve according to claim 1, wherein an annular seal member is disposed between the high pressure side slide valve body and the fitting convex portion of the low pressure side slide valve body.   3. The six-way valve according to claim 2, wherein the outer shape of the annular seal surface of the high pressure side slide valve body on the main valve seat side provided with the three ports is smaller than the outer shape of the seal member. Switching valve.   An inner flange portion is provided on an inner periphery of an end portion on the main valve seat side provided with the three ports in the high pressure side slide valve body, and the annular seal surface is formed on an end surface of the inner valve portion on the main valve seat side The six-way switching valve according to claim 3, characterized in that:   A biasing member is disposed between the high-pressure side slide valve body and the low-pressure side slide valve body to bias the high-pressure side slide valve body and the low-pressure side slide valve body in opposite directions. The six-way switching valve according to any one of claims 2 to 4, characterized in that:   The six-way switching valve according to claim 5, wherein the biasing member is disposed outside the seal member.   The six-way switching valve according to any one of claims 1 to 6, wherein a passage area of the low pressure side U-turn passage is larger than a passage area of the high pressure side U-turn passage.   The guide surface which consists of a bowl-shaped hollow which makes the flow of the high voltage | pressure fluid in the said high voltage | pressure side U turn passage smooth is formed in the end surface of the said fitting convex part. The six-way switching valve according to one item.   First and second variable-volume variable volumes defined by a pair of first and second pistons at one end and the other end of the main valve chamber in the main valve housing, in which high pressure fluid is selectively introduced and discharged. Two working chambers are provided, and the main valve body is axially movably disposed interlockingly with the first and second pistons, and introduction of high pressure fluid to the first and second working chambers A discharge control is performed to move the first and second pistons to move the main valve body in the main valve chamber. The six-way switching valve described in.   The first piston and the second piston can be integrally moved by a connecting body made of one or a plurality of plate members disposed in a direction orthogonal to the valve seat surface of the main valve seat provided with the port Connected to the coupling body so that the main valve body moves along with the reciprocating movement of the first and second pistons, and is slid in a direction perpendicular to the valve seat surface of the main valve seat. The six-way switching valve according to claim 9, characterized in that it is supported freely.   11. The six-way switching valve according to claim 10, wherein the coupling body is provided with a stopper portion for restricting the movement of the main valve body in the axial direction.   The six-way switching valve according to claim 11, wherein the stopper portion is adapted to abut on the main valve housing.

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