JP2019078283A - Slidable selector valve and refrigeration cycle system - Google Patents

Abstract

To provide a slidable selector valve capable suppressing damage of a valve body having a reinforcement pin, and a refrigeration cycle system comprising the slidable selector valve.SOLUTION: A press-fit groove part 251 into which a discoid end part 271 of a reinforcement pin 27 is press-fitted, has connection curve surfaces 251D, 251E for connecting side planes 251A, 251B and an upper plane 251C, and the connection curve surfaces 251D, 251E are formed into an arc shape with the side planes 251A, 251B and the upper plane 251C as tangent lines, so that these surfaces are smoothly connected to each other. Since there is no corner part conventional arts have, it is possible to reduce possibility that when a bowl part 25 deforms, a crack occurs due to concentration of stress, and even in a case where abnormal high differential pressure is applied due to abnormality of a system, etc., a valve member 24 of a valve body can be prevented from damaging.SELECTED DRAWING: Figure 6

Description

  The present invention relates to a slide switch valve and a refrigeration cycle system.

  Heretofore, as a slide type switching valve used in a refrigeration cycle system, one in which a reinforcing pin is provided on a valve body in sliding contact with a valve seat surface has been proposed (see, for example, Patent Document 1). In the valve body described in Patent Document 1, the concave portion is formed at four places of the sliding portion, so that the stress generated on the contact surface with the valve seat is uniform even when the reinforcing pin is provided. It is supposed to be

JP 2012-82883 A

  As described in Patent Document 1, in the configuration in which the reinforcing pin is provided on the valve body, the reinforcing pin is pressed into the groove formed on the valve body, and the corner portion is formed in the groove. There is. Although it is possible to suppress the deformation of the valve body by providing the reinforcing pin on the valve body, the groove in which the reinforcing pin is pressed into the valve body and the periphery thereof become the starting point of the deformation. When a high differential pressure is applied, stress is concentrated at the corner of the groove, and damage such as cracking may occur.

  An object of the present invention is to provide a slide type switching valve capable of suppressing damage to a valve body having a reinforcing pin, and a refrigeration cycle system provided with the slide type switching valve.

  The slide type switching valve according to the present invention comprises a cylindrical valve body, a valve seat having a valve seat opening formed on a valve seat surface, and a valve body housed in the valve body and in sliding contact with the valve seat surface. The valve body includes a flange portion concavely opening toward the valve seat, and a reinforcing pin extending in the flange portion in a direction orthogonal to the sliding direction, In each of the positions on the inner surface of the portion facing each other in the orthogonal direction, press-fit groove portions are formed, into which the end portions of the reinforcing pins are press-fit from the valve seat side. A connecting curved surface connecting the side flat and the upper flat, the upper curved flat extending along both the sliding direction and the orthogonal direction, and the connecting curved surface , Said side plane and said upper plane viewed from said orthogonal direction Characterized in that it is formed in a circular arc shape with the tangent.

  According to the present invention, the press-fit groove portion into which the end portion of the reinforcing pin is press-fit has a connection curved surface connecting the side flat and the upper flat, and the connection curved line is a tangent to the side flat and the upper flat. These surfaces are connected smoothly by being formed in the shape of a circular arc. Since the conventional corner is not formed, even if an abnormal high differential pressure is applied due to an abnormality of the system, etc., the stress is concentrated when the buttocks are deformed to reduce the possibility of the occurrence of a crack. And can prevent damage to the valve body. In addition, an "upper plane" means the upper and lower sides when the valve-seat surface side in a valve body is made into the lower side, and the upper and lower sides in a perpendicular direction do not necessarily correspond.

  Furthermore, since the press-in groove has an upper flat surface, the radius of the arc of the connecting curved surface is smaller than the radius of the end of the reinforcing pin, and the end of the reinforcing pin is a pair of side flats and an upper flat with respect to the press-in groove. Abuts at three points, and a gap is formed between the end of the reinforcing pin and the connecting curved surface. As a result, the contact position between the end of the reinforcing pin and the press-fitting groove can be specified, and the pressed-in reinforcing pin can be easily positioned at the regular position. Therefore, while the deformation | transformation suppression effect of the valve body by a reinforcement pin is exhibited stably, the dispersion | variation in a flow volume is also suppressed by the position of a reinforcement pin being stable.

  Under the present circumstances, in the slide type switching valve of this invention, it is preferable that the radius of the circular arc of the said connection curved surface is 0.5 times or more of the radius of the edge part of the said reinforcement pin. According to such a configuration, by making the radius of the connecting curved surface large (reducing the curvature), it is possible to suppress concentration of stress on the connecting curved surface when the ridge portion is deformed. That is, if the radius of the arc of the connecting curved surface is too small, the shape becomes close to the corner, and the effect of suppressing stress concentration is reduced.

  Furthermore, in the slide type switching valve according to the present invention, it is preferable that the dimension in the slide direction of the upper plane is 0.05 times or more of the distance between the pair of side planes. According to such a configuration, it is possible to ensure the sliding direction dimension of the upper plane and to make it easy to make contact with the end of the reinforcing pin, and to easily secure the gap between the end of the reinforcing pin and the connection curved surface . On the other hand, when the dimension in the sliding direction of the upper surface is too small or when the upper surface is not formed, the end of the reinforcing pin and the connection curved surface come into contact (a gap is not formed) due to dimensional error or the like. There is. In this case, the contact position between the end of the reinforcing pin and the press-fitting groove becomes difficult to identify, and the pressed-in reinforcing pin may deviate from the normal position, and the deformation suppressing effect of the valve pin by the reinforcing pin is stable It becomes difficult to be exhibited, and the flow rate may vary due to the variation of the position of the reinforcing pin.

  The refrigeration cycle system of the present invention comprises a compressor for compressing a refrigerant that is a fluid, a first heat exchanger that functions as a condenser in the cooling mode, and a second heat exchanger that functions as an evaporator in the cooling mode. An expansion means for expanding and reducing the pressure by expanding the refrigerant between the first heat exchanger and the second heat exchanger, and the slide type switching valve according to any one of the above. According to the present invention as described above, even if an abnormal high differential pressure is applied due to a system abnormality or the like, damage to the valve body can be suppressed, and fluid leakage from the damaged part can be prevented. Can be suppressed, and a decrease in the operating efficiency of the refrigeration cycle system can be suppressed.

  According to the slide type switching valve and the refrigeration cycle system of the present invention, the side flat surface of the press-in groove and the upper flat surface are connected by the arc-shaped connection curved surface, so an abnormal high differential pressure is applied due to an abnormality of the system. Even in this case, stress concentration around the end portion of the press-fit reinforcing pin can be alleviated to suppress damage to the valve body.

It is a schematic block diagram of the refrigerating cycle provided with the slide type switching valve concerning one embodiment of the present invention. It is a sectional view showing the slide type switching valve. It is sectional drawing which expands and shows the principal part of the valve body of the said slide type switching valve. It is a bottom view which shows the principal part of the said valve body. It is sectional drawing which shows the principal part of the said valve body. It is a side view which shows an example of the preferable form of the pressing-in groove part of the said valve body. It is a side view which shows another example of the preferable form of the pressing-in groove part of the said valve body. It is a side view which shows another example of the preferable form of the pressing-in groove part of the said valve body.

  Hereinafter, embodiments of the present invention will be described based on the drawings. The four-way switching valve (slide type switching valve) 10 of the present embodiment is provided, for example, in the refrigeration cycle 1 as shown in FIG. The refrigeration cycle 1 is used for an air conditioner such as a room air conditioner, and is a compressor 2 that compresses a refrigerant as a fluid, and outdoor heat as a first heat exchanger that functions as a condenser in a cooling mode. The refrigerant is expanded and decompressed between the exchanger 3, the indoor heat exchanger 4 as a second heat exchanger functioning as an evaporator in the cooling mode, and the outdoor heat exchanger 3 and the indoor heat exchanger 4. An expansion valve 5 as expansion means, a four-way switching valve 10, and a pilot solenoid valve 6 for switching control of the flow path of the four-way switching valve 10 are connected, and they are connected by a refrigerant pipe. The expansion means is not limited to the expansion valve 5 but may be a capillary.

  The refrigeration cycle 1 has a compressor 2, a four-way switching valve 10, an outdoor heat exchanger 3, an expansion valve 5, an indoor heat exchanger 4, a four-way switching valve 10, and a compressor in the cooling mode (cooling operation) shown in FIG. A cooling cycle in which the refrigerant flows in the order of 2 is configured. On the other hand, in the heating mode (heating operation), the heating in which the refrigerant flows in the order of the compressor 2, the four-way switching valve 10, the indoor heat exchanger 4, the expansion valve 5, the outdoor heat exchanger 3, the four-way switching valve 10 and the compressor 2. Configure the cycle. The switching between the heating cycle and the cooling cycle is performed by the switching operation of the four-way switching valve 10 by the pilot solenoid valve 6.

  The four-way switching valve 10 according to the embodiment of the present invention includes a cylindrical valve body 11, a valve body 12 slidably provided inside the valve body 11, and a compressor 2 as shown in FIG. 2. The high pressure side conduit (D joint) 13 as a joint member in communication with the discharge port of the second embodiment, the low pressure side conduit (S joint) 14 in communication with the suction port of the compressor 2, and the indoor side conduit in communication with the indoor heat exchanger 4 (E joint) 15 and an outdoor side conduit (C joint) 16 communicating with the outdoor heat exchanger 3 are configured. In the present embodiment, the sliding direction of the valve body 12 is the X direction, the extending direction of the conduits 13 to 16 is the Z direction, and the direction orthogonal to the X direction and the Z direction is the Y direction.

  The cylindrical valve body 11 has a plug body 17, 18 for closing both axial end portions thereof, and a valve seat 19 fixed inside the valve body 11, and is configured as a cylinder sealed in its entirety. There is. Conduits 17A and 18A communicated with the pilot solenoid valve 6 are connected to the plugs 17 and 18, respectively. The respective ends of the low pressure side conduit 14, the indoor side conduit 15, and the outdoor side conduit 16 are inserted into the valve seat 19, and openings forming the first port 11C, the second port 11D, and the outflow port 11B described later. Is provided. The upper surface 19A of the valve seat 19 serves as a guide surface (valve seat surface) for slidingly guiding the valve body 12.

  The valve body 11 is formed with a plurality of ports 11A, 11B, 11C, 11D opened in the side surface portion 111 thereof. That is, the inflow port 11A as an opening to which the high pressure side conduit 13 is connected to allow the refrigerant to flow into the valve main body 11, and the valve on the side opposite to the inflow port 11A in the radial direction of the side surface portion 111 of the valve main body 11. A first port 11C, a second port 11D and an outflow port 11B as valve seat openings formed on the upper surface 19A of the seat 19 are provided. The outflow port 11B is provided substantially at the center in the axial direction of the valve body 11, and the first port 11C is provided adjacent to one side (left side in FIG. 2) of the outflow port 11B along the axial direction of the valve body 11. The second port 11D is provided on the other side (right side in FIG. 2) of the outflow port 11B along the axial direction of the valve body 11. That is, the three ports 11B to 11D are provided to be aligned in a straight line.

  The low pressure side conduit 14 is connected to the outflow port 11B, and the indoor side conduit 15 is connected to the first port 11C, so that the first port 11C constitutes an indoor side port, and the second port 11D is outdoor side. By the conduit 16 being connected, the second port 11D constitutes an outdoor side port. The low pressure side conduit 14, the indoor side conduit 15 and the outdoor side conduit 16 are fixed by brazing to the valve body 11 and the valve seat 19 around the outlet port 11B and the first and second ports 11C and 11D, respectively.

  The valve body 12 includes a pair of left and right pistons 21 and 22 in sliding contact with the inner peripheral surface of the valve main body 11, and a connecting member 23 which connects the pair of pistons 21 and 22 and extends along the axial direction of the valve main body 11. The valve member 24 has a hook-shaped valve member 24 supported by the connecting member 23 and a reinforcing pin 27 for reinforcing the valve member 24. The internal space of the valve body 11 includes a high pressure chamber R1 formed between the pair of pistons 21 and 22, a first working chamber R2 formed between one of the pistons 21 and the plug 17, and the other. A second working chamber R3 formed between the piston body 22 and the plug 18 is partitioned.

  The connection member 23 is made of a metal plate material, extends along the axial direction of the valve main body 11, extends in parallel to the upper surface 19A of the valve seat 19, and one end of the connection plate 23A is bent. It is formed to have a fixed piece portion 23B fixed to the piston body 21 and a fixed piece portion 23C bent at the other end of the connecting plate portion 23A and fixed to the piston body 22. In the connecting plate portion 23A, a holding hole 23D for holding the valve member 24 and two through holes 23E for circulating the refrigerant are formed.

  The valve member 24 is an integrally formed member made of synthetic resin, and has a flange portion 25 which opens in a concave shape toward the valve seat 19 and a flange portion 26 extending outward from the opening edge of the flange portion 25. It is formed. The collar portion 25 is formed in a dome shape having an oval shape in a plan view, and is inserted into the holding hole 23D of the connecting member 23. In the inside of the collar portion 25, the outflow port 11B and the first port 11C are communicated and the second port 11D is not communicated, or the outflow port 11B and the second port 11D are communicated and the first port 11C is communicated. A communication space R4 is formed to prevent communication.

  The flange portion 26 has, on its lower surface (surface facing the upper surface 19A of the valve seat 19) 260, a sliding contact surface 26A in sliding contact with the upper surface 19A and a valve opening 25A communicating with the inside of the collar 25. The flange portion 26 is disposed between the valve seat 19 and the connecting member 23. Then, the sliding contact surface 26A is brought into close contact with the upper surface 19A of the valve seat 19 by the pressure difference between the high pressure and the low pressure acting on the valve member 24, and the communication space R4 of the flange 25 is closed to the valve seat 19. There is.

  As shown in FIGS. 3 to 5, the reinforcing pin 27 is formed of a metal material such as stainless steel, and is disposed in the collar 25 and extends along the Y direction. The reinforcing pin 27 integrally includes a pair of disc-shaped end portions 271 provided at both ends thereof and a pin main body 272 extending in a rod shape between the pair of disc-shaped end portions 271. The end portion 271 is formed larger in diameter than the pin main body 272. In addition, the shape of a reinforcement pin is arbitrary, for example, you may use that by which the whole was formed in cylindrical shape (The end part and a center part have an equal outer diameter).

  The flange portion 25 is formed with a pair of press-fit grooves 251 for press-fitting the disc-like end 271. The pair of press-fit grooves 251 are formed at positions opposite to each other in the Y direction in the inner surface (the surface along the ZX plane) 250 of the collar 25 and near the lower surface 260 in the substantially central portion in the X direction and the Z direction. Is located in The press-in groove portion 251 is formed in a concave shape as viewed from the inside of the collar portion 25 while the lower surface 260 side is opened in the Z direction. With such a configuration, the disc-like end 271 is press-fit into the press-fit groove 251 from the lower surface 260 side with the Z direction as the press-fit direction. When the reinforcing pin 27 is attached to the collar 25, the disk-like end 271 abuts against the inner surface 250 of the collar 25 and the collar 25 is compressed by the external force in the Y direction (caused by the pressure difference between the inside and the outside It is suppressed that it is deformed by external force). In the present embodiment, the length of the reinforcing pin 27 is slightly longer than the distance between the inner surfaces 251F of the press-fit groove 251 in the pair of inner surfaces 250, but the upper side of the pair of inner surfaces 250 (lower surface 260 And the distance between the inner surfaces 251 F may be shorter than the distance between the portions on the opposite side of

  In the four-way switching valve 10 described above, when high-pressure refrigerant is introduced into the second working chamber R3 via the pilot solenoid valve 6 and the conduit 18A, as shown in FIGS. 12 is slid to one side (left side in FIGS. 1 and 2) of the valve body 11 in the axial direction (the parallel direction of the ports 11B to 11D) and moved to the first position. Further, when the high pressure refrigerant discharged from the compressor 2 is introduced into the first working chamber R2 via the pilot solenoid valve 6 and the conduit 17A, the piston body 21 is pressed and the valve body 12 is in the axial direction of the valve body 11 It is slid to the other side (right side in FIGS. 1 and 2) and moved to the second position.

  When the valve body 12 is in the second position, the flange portion 25 of the valve member 24 brings the outflow port 11B into communication with the second port 11D by the communication space R4. Further, since the flange portion 25 is positioned on the other side of the first port 11C, the first port 11C is in communication with the inflow port 11A via the inside (high pressure chamber R1) of the valve main body 11. That is, when the valve body 12 is in the second position, the heating mode (heating operation) is established in which the inflow port 11A and the first port 11C are in communication and the outflow port 11B and the second port 11D are in communication.

  In this heating mode, the high pressure refrigerant H discharged from the compressor 2 is introduced into the high pressure chamber R1 via the high pressure side conduit 13 and the inflow port 11A, and the high pressure refrigerant H passing through the high pressure chamber R1 is the first port 11C. And the indoor heat exchanger 4 via the indoor side conduit 15. Further, the low pressure refrigerant L is introduced from the outdoor heat exchanger 3 into the communication space R4 of the brim portion 25 through the outdoor side conduit 16 and the second port 11D, and the low pressure refrigerant L passing through the communication space R4 is the outflow port 11B and It is returned to the compressor 2 via the low pressure side conduit 14.

  On the other hand, when the valve body 12 is in the first position, the flange portion 25 of the valve member 24 causes the communication port R4 to communicate the outflow port 11B with the first port 11C. Further, since the flange portion 25 is located on one side of the second port 11D, the second port 11D is in communication with the inflow port 11A via the inside (high pressure chamber R1) of the valve main body 11. That is, when the valve body 12 is at the first position, the cooling mode (cooling operation) is established in which the inflow port 11A and the second port 11D are in communication and the outflow port 11B and the first port 11C are in communication.

  Here, details of the shape and dimensions of the press-fit groove portion 251 will be described with reference to FIG. FIG. 6 is a view of the periphery of the press-fit groove 25 of the collar 25 as viewed from the inside. The press-fit groove portion 251 is a connection curved surface connecting a pair of side flat surfaces 251A, 251B extending along the Y direction and the Z direction, an upper flat surface 251C extending along the X direction and the Y direction, the side flat surface 251A and the upper flat surface 251C. A connection curved surface 251E connecting the side flat surface 251B and the upper flat surface 251C, and an inner surface 251F. The side planes 251A, 251B extend along the YZ plane, and the upper plane 251C extends along the XY plane, but may have some inclination.

  The connection curved surface 251D is formed in an arc shape having a side flat surface 251A and an upper flat surface 251C as tangent lines when viewed from the Y direction. Similarly, the connection curved surface 251E is formed in an arc shape having a side flat surface 251B and an upper flat surface 251C as tangent lines when viewed from the Y direction. The press-in groove portion 251 passes near the central portion in the X direction and is formed plane-symmetrically with a plane parallel to the YZ plane as a symmetrical plane, and the following mainly describes the side plane 251A and the connecting curved surface 251D. The side plane 251B and the connecting curved surface 251E also have similar shapes and dimensions.

  The disc-like end 271 is press-fit into the press-fit groove 251, so that its diameter 2R is formed equal to or slightly larger than the distance (groove width) H between the pair of side planes 251A and 251B. It is assumed that = H. The depth (dimension in the Z direction) of the press-in groove portion 251 may be 2R or more in diameter.

  The radius r of the arc of the connecting curved surface 251D is 0.5 times or more and less than 1 time the radius R of the disc-like end 271. Thus, the disc-like end 271 contacts the side flat surface 251A and the upper flat surface 251C, and is separated from the connection curved surface 251D to form the gap. Further, the dimension h in the X direction of the upper flat surface 251C is 0.05 times or more of the groove width H. That is, the radius r of the arc of the connecting curved surface 251D is 0.95 times or less the radius R of the disc-like end 271. Three examples are shown in FIGS. 6-8 about the press-fit groove part 251 which satisfy | fills such a dimension.

  In the example shown in FIG. 6, the radius r of the arc of the connecting curved surface 251D is 0.7 times the radius R of the disc-like end 271. That is, the radius r is 0.35 times the groove width H. Further, the dimension h in the X direction of the upper flat surface 251C is 0.3 times the diameter 2R of the disk-shaped end 271.

  In the example shown in FIG. 7, the radius r of the arc of the connecting curved surface 251 D is 0.5 times the radius R of the disc-like end 271, and the radius r is 0.25 times the groove width H. The dimension h of the upper flat surface 251C in the X direction is 0.5 times the diameter 2R of the disc-like end 271.

  In the example shown in FIG. 8, the radius r of the arc of the connecting curved surface 251 D is 0.95 times the radius R of the disc-like end 271, and the radius r is 0.475 times the groove width H. The dimension h of the upper flat surface 251C in the X direction is 0.05 times the diameter 2R of the disc-like end 271.

  According to such an embodiment, the following effects can be obtained. That is, the press-in groove portion 251 into which the disc-like end 271 of the reinforcing pin 27 is press-fitted has connecting curved surfaces 251D and 251E connecting the side flats 251A and 251B and the upper flat 251C, and the connecting curved surfaces 251D and 251E. Are formed in an arc shape tangent to the side flat surfaces 251A, 251B and the upper flat surface 251C, these surfaces are connected smoothly. As the conventional corner portion (shown by a two-dot chain line in FIG. 6) is not formed, even when an abnormal high differential pressure is applied due to a system abnormality or the like, the stress The possibility of concentration and cracking can be reduced, and damage to the valve member 24 of the valve body 12 can be suppressed.

  Furthermore, since the press-fit groove 251 has the upper flat surface 251C, the radius r of the arc of the connection curved surfaces 251D, 251E is smaller than the radius R of the disc-like end 271, and the disc-like end 271 On the other hand, it abuts at three points of the pair of side flat surfaces 251A, 251B and the upper flat surface 251C, and a gap 28 is formed between the disk-like end 271 and the connection curved surface 251D, 251E. Thereby, the contact position of the disk-shaped end 271 and the press-fit groove portion 251 can be specified, and the press-fitted reinforcing pin 27 can be easily positioned at the regular position. Accordingly, the effect of suppressing the deformation of the valve member 24 in the valve body 12 by the reinforcing pin 27 is stably exhibited, and the position of the reinforcing pin 27 is also stabilized, so that the variation in the flow rate is also suppressed.

  Furthermore, the radius r of the arc of the connection curved surfaces 251D, 251E is 0.5 times or more the radius R of the disk-like end 271 and the ridge 25 is deformed by increasing the radius r (reducing the curvature) It is possible to suppress concentration of stress on the connection curved surfaces 251D and 251E. That is, if the radius r of the arc of the connection curved surfaces 251D and 251E is too small, the shape becomes close to the corner, and the effect of suppressing stress concentration is reduced.

  In addition, the dimension in the X direction of the upper flat surface 251C is 0.05 times or more of the groove width H, and by ensuring the dimension in the X direction of the upper flat surface 251C, the disc-shaped end 271 can be easily contacted. The gap 28 can be easily secured between the disk-shaped end 271 and the connection curved surfaces 251D and 251E. On the other hand, when the dimension of the upper flat surface 251C in the X direction is too small or when the upper flat surface 251C is not formed, the disk-like end 271 and the connection curved surfaces 251D and 251E contact with each other. The gap 28 may not be formed. In this case, the contact position between the disc-like end and the press-fit groove becomes difficult to identify, and the press-fit reinforcing pin may be deviated from the normal position. It becomes difficult to be stably exhibited, and the flow rate may vary due to the variation of the position of the reinforcing pin.

  In addition, even if the refrigeration cycle 1 is subjected to an abnormal high differential pressure due to a system abnormality or the like as described above, the four-way switching valve 10 capable of suppressing damage to the valve member 24 of the valve body 12 By providing, the leak of the fluid from the damaged part can be suppressed, and the fall of the operating efficiency of the refrigeration cycle 1 can be suppressed.

  In addition, this invention is not limited to the said embodiment, The other modification etc. which can achieve the objective of this invention are included, and the modification as shown below is also included in this invention.

  For example, in the embodiment, the radius r of the arc of the connection curved surface 251D is 0.5 times or more the radius R of the disk-like end 271 and the dimension h in the X direction of the upper flat surface 251C is 0.05 of the groove width H The radius of the arc of the connecting curved surface may be less than 0.5 times the radius of the disc-like end depending on the size, shape, etc. of the ridges and reinforcing pins. The X-direction dimension of the plane may be less than 0.05 times the groove width. For example, if the reinforcing pin is large enough and the radius of the discoid end is also large, the radius of the arc of the connecting curved face is less than 0.5 times the radius of the discoid end. The absolute value of can be secured, and stress concentration can be suppressed. In addition, when the radius of the disc-like end is sufficiently large and the groove width is also wide, even if the dimension in the X direction of the upper plane is less than 0.05 times the groove width, between the connection curved surface and the disc-like end Can form a gap of sufficient size.

  Besides, the best configuration, method and the like for carrying out the present invention are disclosed in the above description, but the present invention is not limited to this. That is, although the present invention has been particularly illustrated and described primarily with respect to particular embodiments, it should be understood that the present invention may be configured relative to the above-described embodiments without departing from the scope of the inventive concept and object. Those skilled in the art can make various modifications in materials, quantities, and other detailed configurations. Therefore, the description with the above-described disclosure of the shape, the material, etc. is exemplarily described for facilitating the understanding of the present invention, and is not intended to limit the present invention. The description in the name of a member from which some or all of the limitations such as the limitation have been removed is included in the present invention.

1 refrigeration cycle 2 compressor 3 outdoor heat exchanger (first heat exchanger)
4 Indoor heat exchanger (second heat exchanger)
5 Expansion valve (expansion means)
10 Four-way switching valve (slide type switching valve)
11 valve body 12 valve body 24 valve member 25 flange 250 inner surface 251 press-fit groove 251A, 251B side flat surface 251C upper flat surface 251D, 251E connection curved surface 27 reinforcing pin 271 disk-shaped end

Claims (4)

A slide type switching valve comprising a cylindrical valve body, a valve seat having a valve seat opening formed on a valve seat surface, and a valve body housed in the valve body and in sliding contact with the valve seat surface. ,
The valve body includes a hook portion concavely opening toward the valve seat, and a reinforcing pin extending in a direction orthogonal to the sliding direction in the hook portion,
At each of the positions on the inner surface of the flange facing in the orthogonal direction, press-fit groove portions are formed in which the end portions of the reinforcing pins are press-fit from the valve seat side,
The press-fit groove portion connects a pair of side planes extending along both the press-in direction and the orthogonal direction, an upper plane extending along both the sliding direction and the orthogonal direction, the side plane and the upper plane Connection surface, and
The sliding switching valve according to claim 1, wherein the connection curved surface is formed in an arc shape tangent to the side plane and the upper plane when viewed from the orthogonal direction.   The slide switching valve according to claim 1, wherein the radius of the arc of the connection curved surface is 0.5 times or more of the radius of the end of the reinforcing pin.   The slide type switching valve according to claim 1 or 2, wherein the dimension of the upper plane in the slide direction is 0.05 times or more of the distance between the pair of side planes.   A compressor that compresses a refrigerant that is a fluid, a first heat exchanger that functions as a condenser in the cooling mode, a second heat exchanger that functions as an evaporator in the cooling mode, the first heat exchanger, and the first heat exchanger A refrigeration cycle system comprising expansion means for expanding a refrigerant between two heat exchangers and reducing the pressure, and the slide type switching valve according to any one of claims 1 to 3.

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