Slide-type selector valve and refrigerating cycle system

Abstract

To provide a slide-type selector valve and a refrigerating cycle system capable of improving durability against collision load when a piston contacts a stopper part of a lid member.SOLUTION: A lid member 12 in a valve housing of a slide-type selector valve includes: a lid body part 121; a stopper part 122 which protrudes from the lid body part 121 in a flange-like manner, and contacts and receives a piston 221 of a slide mechanism 22; and impact stress relaxing means relaxing stress caused by impact when the piston 221 contacts the stopper part 122. The impact stress relaxing means is provided with an impact stress relaxing part 123 which cylindrically protrudes in an axial direction from an outer peripheral edge 122b of the stopper part 122 between the stopper part 122 and an opening end 11b of a valve body 11, has a protrusion end edge 123a abutted to the opening end 11b of the valve body 11, and is fixed to the opening end 11b.SELECTED DRAWING: Figure 4

Description

[Technical field]

[0001] The present invention relates to a slide-type switching valve used in a refrigeration cycle system of an air conditioner or the like for switching a flow path of a refrigerant, and to a refrigeration cycle system. [Background technology]

[0002] Conventionally, a slide-type switching valve is known in which a valve body is housed inside a valve housing in which the openings at both ends of a cylindrical valve body are closed with a cover member (see, for example, Patent Document 1). In the slide-type switching valve described in Patent Document 1, the valve body is connected to a slide mechanism that moves inside the valve housing by receiving a slide driving force from a piston, and the valve body moves together with the slide mechanism. Here, in this slide-type switching valve, the cover member includes a lidded cylindrical cover main body portion and a flange-like portion that protrudes in a flange-like manner and is fixed to the open end of the valve body near the outer periphery. A part of the flange-like portion of the cover member protrudes toward the inside of the valve body near the inner periphery, and the protruding surface portion serves as a stopper portion against which the piston of the slide mechanism that moves together with the valve body abuts and is received. [Prior art documents] [Patent documents]

[0003] [Patent Document 1] JP 2023-120826 A Summary of the Invention [Problem to be solved by the invention]

[0004] In the above-mentioned slide-type switching valve, when the piston abuts against the stopper, the impact load is transmitted to the fixed portion between the open end of the valve body and the flange of the cover member, and stress is generated in the axial direction to peel off the flange of the cover member from the open end of the valve body. Here, in recent years, ultra-high pressure fluids such as CO2 are sometimes used as the fluid in refrigeration cycle systems that apply a sliding driving force to the piston, and in this case, the impact load when the piston abuts against the stopper may be excessive. Therefore, there is a demand for improving durability against such excessive impact loads.

[0005] An object of the present invention is to provide a slide type switching valve and a refrigeration cycle system capable of improving durability against a collision load when a piston abuts against a stopper portion of a cover member. [Means for solving the problem]

[0006] The slide type switching valve of the present invention comprises a valve housing having a cylindrical valve body with at least one pair of pipes connected to its peripheral wall, and each opening at both ends of the valve body being closed with a cover member; a valve body installed inside the valve body so as to be slidable in the axial direction of the valve body and switching the communication state of the pipes; and a slide mechanism extending in the axial direction inside the valve body and having pistons at both ends, the valve body being connected to an intermediate portion of the slide mechanism and receiving a slide driving force in the axial direction from the pistons to slide the valve body, wherein the cover member is formed in a covered cylindrical shape having an inner diameter smaller than the inner diameter of the opening of the valve body, and is disposed outside the opening of the valve body in the axial direction so that the cylindrical opening faces the opening of the valve body; the valve body having a surface facing the opening and a surface facing the opening that abuts against and receives the piston at one end side of the slide mechanism as it slides through the opening in the axial direction; and an impact stress mitigation means for mitigating stress caused by the impact when the piston abuts against the stopper portion, the impact stress mitigation means being characterized in that the impact stress mitigation means is a means for mitigating the stress by providing an impact stress mitigation portion that protrudes in a cylindrical shape in the axial direction from the outer circumferential edge of the stopper portion between the stopper portion and an opening end surrounding the opening of the valve body, the protruding edge of which abuts against the opening end of the valve body and is fixed to the opening end. In addition to providing the impact stress mitigation portion, the impact stress mitigation means may also serve as a means for mitigating the stress by causing the stopper portion to flex and deform in the axial direction and the impact stress mitigation portion to flex and deform in a direction intersecting the axial direction due to the impact when the stopper portion comes into contact with the piston.

[0007] In this slide-type switching valve, an impact stress mitigation means is provided in the cover member between the stopper portion against which the piston of the slide mechanism abuts and the protruding end edge fixed to the open end of the valve body, which mitigates stress generated in the fixed portion between the valve body and the cover member due to the impact when the piston abuts. According to this impact stress mitigation means, the stopper portion is disposed at a position away from the fixed portion between the valve body and the cover member in the axial direction of the valve body by providing the impact stress mitigation means between the stopper portion and the open end of the valve body. As a result, even when the piston abuts against the stopper portion with a large impact load due to the use of an ultra-high pressure fluid in the refrigeration cycle system, the stress acting on the fixed portion between the valve body and the cover member is mitigated. In other words, the impact load at the time of abutment is less likely to directly act on the fixed portion between the open end of the valve body and the cover member as a stress that tries to separate them, so that durability against the impact load when the piston abuts against the stopper portion of the cover member can be improved. In addition, by configuring the impact stress absorbing means as a means for absorbing stress by bending and deforming the stopper portion in the axial direction and the impact stress absorbing portion in the transverse direction, it is possible to further reduce the direct effect of the collision load on the fixed portion upon contact, thereby further improving durability against the collision load.

[0008] Here, when the length of the cylindrical impact stress absorbing portion in the axial direction is L and the thickness of the cylindrical wall is T, 0.5T≦L It is preferable that the above relationship is satisfied.

[0009] According to this configuration, by making the axial length of the impact stress absorbing portion sufficiently long and by configuring the stopper portion to be positioned at a position sufficiently far outwardly in the axial direction from the fixed portion between the valve body and the cover member, stress at the fixed portion between the valve body and the cover member can be more effectively mitigated.

[0010] Moreover, the impact stress absorbing portion further comprises: L≦5T It is more preferable that the above relationship is satisfied.

[0011] According to this configuration, it is possible to effectively relieve stress while preventing the cover member including the impact stress absorbing portion, that is, the slide type switching valve, from becoming large.

[0012] It is also preferable that the impact stress mitigating portion is provided with a small-diameter cylindrical protrusion which protrudes in the axial direction from a position near the inner circumference of the protruding end edge toward the opening side of the valve body in a cylindrical shape having a diameter smaller than the outer diameter of the impact stress mitigating portion, or a small-diameter recess which is recessed in the axial direction from a position near the inner circumference of the protruding end edge toward the stopper portion to a diameter smaller than the outer diameter of the impact stress mitigating portion, and that the opening end of the valve body is provided with a positioning recess, near the inner circumference of the opening end, into which the small-diameter cylindrical protrusion of the impact stress mitigating portion is fitted to position the cover member when it is attached, or a positioning convex portion, near the inner circumference of the opening end, which is fitted into the small-diameter recess of the impact stress mitigating portion to position the cover member when it is attached.

[0013] With this configuration, the cover member is positioned with respect to the opening of the valve body by fitting the small diameter cylindrical protrusion into the positioning recess, or by fitting the positioning convex portion into the small diameter recess, so that the subsequent fixing work can be carried out with good workability.

[0014] It is further preferable that the fixed portion is a welded portion formed by welding the protruding end edge to the opening end of the valve body from the outer peripheral surface side of the valve body, and is formed with a weld depth that does not penetrate the small diameter cylindrical protrusion or the positioning convex portion in the thickness direction.

[0015] According to this configuration, the welded portion as the fixed part is formed with a welding depth that does not penetrate in the thickness direction through the small diameter cylindrical protrusion on the cover member or the positioning convex portion on the valve body, thereby effectively preventing spatter from entering the inside of the valve body during welding.

[0016] The refrigeration cycle system of the present invention is characterized by comprising a compressor that compresses a refrigerant which is a fluid, a first heat exchanger that functions as a condenser in a cooling mode, a second heat exchanger that functions as an evaporator in the cooling mode, an expansion means that expands the refrigerant between the first heat exchanger and the second heat exchanger to reduce its pressure, and the above-mentioned sliding switching valve.

[0017] According to this refrigeration cycle system, since the above-mentioned slide type switching valve is provided, it is possible to improve durability against a collision load when the piston abuts against the stopper portion of the lid member. Effect of the Invention

[0018] According to the slide type switching valve and the refrigeration cycle system of the present invention, it is possible to improve durability against a collision load when the piston abuts against the stopper portion of the lid member. [Brief description of the drawings]

[0019] [Figure 1] 1 is a cross-sectional view showing a cross section along an axial direction of a valve housing of a slide type switching valve according to one embodiment. [Diagram 2] 2 is an enlarged cross-sectional view of the cover member shown in FIG. 1. FIG. [Diagram 3] 2 is a diagram illustrating the end structure on the right side of the slide type switching valve illustrated in FIG. 1 in a state in which the piston abuts against a stopper portion of a lid member. FIG. [Figure 4] FIG. 4 is an enlarged view showing an area A11 in FIG. [Diagram 5] FIG. 5 is a schematic diagram showing a refrigeration cycle system including the slide type switching valve shown in FIGS. 1 to 4. [Figure 6] 5 is a graph showing the change in stress relaxation effect when the axial length L is changed relative to the thickness T of the cylindrical wall for the impact stress relaxation portion shown in FIG. 4, for various cylindrical wall thicknesses T. [Figure 7]6 is a diagram showing, with an enlarged cross section similar to that of FIG. 4, first to third modified examples of the impact stress absorbing portion shown in FIG. 4, which are expected to have a stress absorbing effect from the graph shown in FIG. [Figure 8] 6 is a diagram showing, with an enlarged cross section similar to that of FIG. 4, fourth to sixth modified examples of the impact stress absorbing portion shown in FIG. 4, which are expected to have a stress absorbing effect from the graph shown in FIG. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0020] BEST MODE FOR CARRYING OUT THE DISCLOSURE Hereinafter, a slide type switching valve and a refrigeration cycle system according to one embodiment of the present invention will be described with reference to Figs.

[0021] FIG. 1 is a cross-sectional view showing a cross section along the axial direction of a valve housing of a slide type switching valve of one embodiment. FIG. 2 is an enlarged view of a cross section of a cover member shown in FIG. 1. FIG. 3 is a view showing an end structure on the right side in the drawing in the slide type switching valve shown in FIG. 1 in a state where a piston abuts against a stopper portion of the cover member, and FIG. 4 is an enlarged view showing an area A11 in FIG. 3. FIG. 5 is a schematic diagram showing a refrigeration cycle system including the slide type switching valve shown in FIGS. 1 to 4. In the following description, in FIGS. 1 and 5, the side where the E joint pipe 13e is shown is called the left side, and the side where the C joint pipe 13c is shown is called the right side.

[0022] As shown in FIG. 1, the slide type switching valve 10 of this embodiment is a four-way switching valve that switches the communication state of four pipes, and has a structure in which a slide valve body 2 is provided inside a valve housing 1.

[0023] The valve housing 1 is a tubular member with both ends closed, and is composed of a cylindrical valve body 11 and two cover members 12. The cover members 12 are attached to the valve body 11 so as to close the openings 11a at both ends of the valve body 11. In this embodiment, the cover member 12 is fixed to the valve body 11 by welding from the outer circumferential surface side of the valve body 11. Regarding this cover member 12, FIG. 2 shows the cover member 12 in a separate state before welding, and FIG. 3 shows the state in which the cover member 12 is welded to the valve body 11, together with a part of the piston 221 of the slide valve body 2.

[0024] The valve body 11 and the cover member 12 are made of metal such as stainless steel or brass. Methods for fixing such metal members together include welding and brazing, but when welding is used as in this embodiment, it is preferable that the valve body 11 and the cover member 12, which are the objects to be fixed, are made of stainless steel. In addition, the central axes of the valve body 11 and the cover member 12 are the axis X of the valve housing 1. Four pipes, namely, a D joint pipe 13d, an E joint pipe 13e, an S joint pipe 13s, and a C joint pipe 13c, the details of which will be described later, are connected to the peripheral wall of the valve housing 1 so as to communicate with the inside of the valve housing 1.

[0025] A valve seat 15 against which the valve element 21 slides is provided on the inner peripheral surface of the valve body 11. This valve seat 15 is disposed in the middle of the valve body 11, and a D joint pipe 13d serving as a high-pressure pipe that opens into the valve body 11 is attached to a position facing the valve seat 15 in the middle of the valve body 11. In addition, a pair of conduits, namely, an E joint pipe 13e and a C joint pipe 13c, and a low-pressure pipe, namely, an S joint pipe 13s, are attached to the valve seat 15, aligned in a straight line in the direction of the axis X of the valve housing 1.

[0026] The slide valve element 2 is a member that is installed inside the valve body 11 so as to be slidable in the axial direction D11 of the valve body 11, and switches the communication state of the above-mentioned four pipes. The slide valve element 2 includes a valve element 21 and a slide mechanism 22.

[0027] The valve body 21 switches the communication state of the above four pipes by sliding in the axial direction D11. The valve body 21 has a bowl-shaped recess 21A formed on its inside. At the left end position of the valve body 21 in FIG. 1, the valve body 21 communicates with the S joint pipe 13s and the E joint pipe 13e through the bowl-shaped recess 21A. At this time, the C joint pipe 13c communicates with the D joint pipe 13d mainly through the through hole 222a of the connecting plate 222 of the slide mechanism 22 in the high pressure chamber 1A partitioned by the pistons 221 at both ends of the slide mechanism 22 inside the valve housing 1. At the right end position of the slide valve body 2 moved to the right in FIG. 1, the valve body 21 communicates with the S joint pipe 13s and the C joint pipe 13c through the bowl-shaped recess 21A. At this time, the E joint pipe 13e communicates with the D joint pipe 13d mainly via the through hole 222a within the high pressure chamber 1A.

[0028] The slide mechanism 22 is a mechanical part extending in the axial direction D11 inside the valve body 11 and having pistons 221 at both ends. The slide mechanism 22 is connected to the valve body 21 at its middle part, and slides the valve body 21 by receiving a slide driving force in the axial direction D11 by the pistons 221. The slide mechanism 22 includes a pair of pistons 221 and a connecting plate 222. Each of the pair of pistons 221 is configured to be approximately disk-shaped and is arranged to sandwich the valve body 21 in the axial direction D11. The connecting plate 222 is a plate member extending in the axial direction D11, and is connected to the middle part of the valve body 21 so that the valve body 21 can slide on the valve seat 15, and the pistons 221 are fixed to both ends. In addition, the connecting plate 222 is provided with one through hole 222a at a position intermediate between the valve body 21 and each piston 221.

[0029] The inside of the valve housing 1 is divided into a high pressure chamber 1A in the center and a first working chamber 1B and a second working chamber 1C located on either side of the high pressure chamber 1A by pistons 221 at both ends of the slide mechanism 22. A driving fluid flows through the first working chamber 1B and the second working chamber 1C from the pilot valve 3 shown in Fig. 5, and the pistons 221 at each end receive a slide driving force via the driving fluid.

[0030] In the refrigeration cycle system 30 shown in FIG. 5, the D joint pipe 13d is a high-pressure pipe connected to the discharge port of the compressor 31, and the S joint pipe 13s is a low-pressure pipe connected to the suction port of the compressor 31. The C joint pipe 13c is a conduit connected to the outdoor heat exchanger 32 (first heat exchanger), and the E joint pipe 13e is a conduit connected to the indoor heat exchanger 33 (second heat exchanger). The outdoor heat exchanger 32 and the indoor heat exchanger 33 are connected via a throttling device 34 (expansion means). The refrigeration cycle system 30 is composed of a path from the C joint pipe 13c to the outdoor heat exchanger 32, the throttling device 34, the indoor heat exchanger 33, and the E joint pipe 13e, and a path from the S joint pipe 13s to the compressor 31 and the D joint pipe 13d. Note that the refrigerant in the refrigeration cycle system 30 contains a small amount of refrigeration oil to protect the compressor 31 and other devices.

[0031] 5 causes the slide valve body 2 to slide in the axial direction D11 by circulating the driving fluid through a pair of spaces sandwiching the slide valve body 2 in the axial direction D11 inside the valve housing 1, i.e., through both the first working chamber 1B and the second working chamber 1C. In this embodiment, the pilot valve 3 causes the slide valve body 2 to slide in the axial direction D11 by circulating the fluid through a D joint pipe 13d as a high-pressure pipe through one of the first working chamber 1B and the second working chamber 1C and circulating the fluid through an S joint pipe 13s as a low-pressure pipe through the other.

[0032] The pilot valve 3 has a structure similar to that of the slide type switching valve 10, and switches the flow path by sliding a pilot valve body inside a pilot valve housing. The pilot valve body switches the communication destination of the low pressure coupling thin tube 14s that communicates with the S coupling tube 13s as a low pressure pipe connected to the suction port of the compressor 31 as follows. That is, the pilot valve body switches the communication destination of the low pressure coupling thin tube 14s between the first housing thin tube 14L connected to the first working chamber 1B of the slide type switching valve 10 and the second housing thin tube 14R connected to the second working chamber 1C. At the same time, the communication destination of the high pressure coupling thin tube 14d that communicates with the D coupling tube 13d as a high pressure pipe connected to the discharge port of the compressor 31 is switched between the second housing thin tube 14R and the first housing thin tube 14L. This generates a pressure difference between the pressure in the first working chamber 1B and the pressure in the second working chamber 1C to which the suction pressure and discharge pressure of the compressor 31 are introduced, and the pressure difference acting on the pair of pistons 221 causes the slide valve body 2 to slide in the axial direction D11 from the high pressure side to the low pressure side. This slide movement switches the position of the valve body 21 in the slide valve body 2, and switches the flow path of the refrigeration cycle system 30.

[0033] With the above configuration, the high-pressure refrigerant compressed by the compressor 31 flows into the high-pressure chamber 1A from the D joint pipe 13d, and in the cooling operation state (cooling mode), the high-pressure refrigerant flows into the outdoor heat exchanger 32 from the C joint pipe 13c. In addition, in the heating operation state (heating mode) in which the position of the valve body 21 is switched, the high-pressure refrigerant flows into the indoor heat exchanger 33 from the E joint pipe 13e. That is, in the cooling operation state, as shown by the solid arrow, the refrigerant discharged from the compressor 31 circulates from the C joint pipe 13c to the outdoor heat exchanger 32 to the throttling device 34 to the indoor heat exchanger 33 to the E joint pipe 13e. In this circulation, the outdoor heat exchanger 32 functions as a condenser, and the indoor heat exchanger 33 functions as an evaporator, performing cooling. The throttling device 34 expands the refrigerant between the outdoor heat exchanger 32 and the indoor heat exchanger 33 to reduce its pressure. During heating operation, the refrigerant is circulated in the reverse direction as indicated by the dotted arrows, with the indoor heat exchanger 33 functioning as a condenser and the outdoor heat exchanger 32 functioning as an evaporator, providing heating.

[0034] In this embodiment, the pair of cover members 12 has the following configuration. The pair of cover members 12 have a mirror-symmetrical structure as shown in Fig. 1, and the structure will be described below using the right cover member 12 shown in an enlarged view in Fig. 2 and Fig. 3 as a representative example.

[0035] The lid member 12 is a cylindrical member with a lid including a lid body 121, a stopper 122, and an impact stress buffer 123. The lid body 121 is a part formed in a dome-shaped cylindrical shape with a lid having an inner diameter φ12 smaller than the inner diameter φ11 of the opening 11a of the valve body 11. The lid body 121 is disposed outside the opening 11a of the valve body 11 in the axial direction D11 so that the cylindrical opening 121a faces the opening 11a of the valve body 11. The lid body 121 has a peripheral wall formed with mounting holes 121c for the first housing capillary tube 14L and the second housing capillary tube 14R.

[0036] The stopper portion 122 is a flange-like portion that protrudes from the opening edge 121b of the cylinder opening 121a of the lid main body portion 121 toward the outside of the lid main body portion 121 and has an outer diameter φ13 larger than the inner diameter φ11 of the opening 11a of the valve body 11. In this embodiment, the outer diameter φ13 of the stopper portion 122 is approximately the same as the outer diameter φ14 of the valve body 11. The stopper surface 122a of the stopper portion 122 is a surface facing the opening 11a of the valve body 11, and the piston 221 on one end side of the slide mechanism 22 that has slid through the opening 11a in the axial direction D11 abuts against the stopper surface 122a to restrict the movement of the slide valve body 2 to the right and left in the axial direction D11.

[0037] The impact stress mitigating portion 123 is a portion that protrudes in a cylindrical shape from the outer peripheral edge 122b of the stopper portion 122 in the axial direction D11, and the protruding end edge 123a is abutted against the opening end 11b surrounding the opening 11a of the valve body 11 and fixed to the opening end 11b. As described above, the fixing here is performed by welding. Here, in this embodiment, the stress caused by the impact when the piston 221 abuts against the stopper portion 122 is mitigated by an impact stress mitigating means having two aspects, that is, a means for mitigating the stress by the arrangement of the impact stress mitigating portion 123 and a means for mitigating the stress by the flexural deformation of the stopper portion 122 and the impact stress mitigating portion 123, as described below.

[0038] <Methods for mitigating impact stress> As described above, in conventional slide-type switching valves, when the piston contacts the stopper portion, the collision load at the time of contact is transmitted to the fixed portion between the opening end of the valve body and the flange-shaped portion of the cover member, generating stress in the axial direction that tries to pull the flange-shaped portion of the cover member away from the opening end of the valve body, which could reduce durability against the collision load when the piston contacts the stopper portion.

[0039] In contrast to this, in this embodiment, by employing an impact stress relaxation means in the lid member 12 that relaxes the stress caused by the impact when the piston 221 abuts against the stopper portion 122, it is possible to eliminate the conventional problem (when the piston abuts against the stopper portion, stress is generated that tries to peel the flange-shaped portion of the lid member from the fixed portion between the valve body and the lid member) and to improve durability against the collision load when the piston 221 abuts against the stopper portion 122. Here, the impact stress relaxation means in this embodiment has impact stress relaxation means (1) (arrangement of the impact stress relaxation portion) and impact stress relaxation means (2) (flexural deformation) as described above, and will be described in order below.

[0040] <Impact stress relaxation means (1) (arrangement of impact stress relaxation part)> The impact stress mitigation means (1) (disposition of the impact stress mitigation part) is a means of providing an impact stress mitigation part 123 between the stopper part 122 and the opening end 11b of the valve body 11, which protrudes from the outer circumferential edge 122b of the stopper part 122 in the axial direction D11 and has a protruding end edge 123a abutting against the opening end 11b of the valve body 11 and fixed to the opening end 11b, as shown in Fig. 3. With this, when the piston 221 abuts against the stopper part 122 with a large collision load due to the use of an ultra-high pressure fluid in the refrigeration cycle system, the stopper part 122 is disposed at a position away from the welded part 16, which is a fixing part between the valve body 11 and the cover member 12, to the outside in the axial direction D11 of the valve body 11. Therefore, since the welded part 16 is less likely to directly act as a stress that tries to peel them apart, durability against the collision load when the piston 221 abuts against the stopper part 122 of the cover member 12 can be improved.

[0041] <Impact stress relief means (2) (deflection deformation)> As described above, the impact stress mitigation means (1) (disposition of the impact stress mitigation portion) can mitigate the stress due to the collision load when the piston 221 abuts against the stopper portion 122 under normal operating conditions. At this time, for example, under high-load operating conditions, the high-low pressure difference becomes large, and the collision load when the piston 221 abuts against the stopper portion 122 may become excessively large. In such a case, the impact stress mitigation means (2) (flexural deformation) further mitigates the stress generated in the welded portion 16 due to the impact when the piston 221 abuts against the stopper portion 122 by the stopper portion 122 flexing and deforming within its elastic range in the axial direction D11 and the impact stress mitigation portion 123 flexing and deforming within its elastic range in the cross direction D12 to the axial direction D11. This mitigation effect of the impact stress mitigation means (2) (flexural deformation) can improve durability against the collision load when the piston 221 abuts against the stopper portion 122 of the cover member 12. 4, the manner in which the impact stress absorbing portion 123 is bent and deformed when the piston 221 comes into contact with the impact stress absorbing portion 123 is shown by dotted lines. The bending deformation shown by the dotted lines is exaggerated for ease of viewing.

[0042] Here, when the length of the cylindrical impact stress absorbing portion 123 in the axial direction D11 is L and the thickness of the cylindrical wall 123b is T, 0.5T≦L (Formula 1) It is preferable that the relationship L≦5T (Formula 2) It is more preferable that the relationship:

[0043] Furthermore, when the thickness of the cylindrical wall 123b of the impact stress absorbing portion 123 is taken as t, it is preferable that the thickness T of the cylindrical wall 123b of the impact stress absorbing portion 123 satisfies the following relationship: 0.5t≦T≦1.5t (Equation 3)

[0044] FIG. 6 is a graph showing the change in stress relaxation effect when the axial length L is changed relative to the thickness T of the cylindrical wall for the impact stress relaxation portion 123 shown in FIG.

[0045] In the graph G shown in Fig. 6, the horizontal axis indicates the ratio of the length L in the axial direction D11 of the impact stress mitigation portion 123 to the thickness T of the cylindrical wall 123b. The vertical axis indicates the stress mitigation effect of the impact stress mitigation portion 123 as a stress ratio when the stress value at L = 0 is set to 100%. The graph G also shows change curves F11, F12, F13, F14, and F15 of the stress ratio versus the length L in the axial direction D11 for five types of impact stress mitigation portions 123 having different ratios of the thickness T of the cylindrical wall 123b to the thickness t of the cylindrical wall 111 in the valve body 11. It can be seen from these change curves F11, F12, F13, F14, and F15 that when 0.5T ≤ L is satisfied, the stress ratio drops to 1.0 or less, i.e., the stress mitigation effect is prominent. In addition, it can be seen from the stress ratio change curves F11, F12, F13, F14, and F15 that such a change in the stress relaxation effect is effectively manifested when 0.5t≦T≦1.5t is satisfied.

[0046] FIG. 7 is a diagram showing, in an enlarged cross section similar to FIG. 4, first to third modified examples of the impact stress mitigation part 123 shown in FIG. 4, which are expected to have a stress mitigation effect from the graph shown in FIG. 6. FIG. 8 is a diagram showing, in an enlarged cross section similar to FIG. 4, fourth to sixth modified examples of the impact stress mitigation part 123 shown in FIG. 4, which are expected to have a stress mitigation effect from the graph shown in FIG. 6. In FIG. 7 and FIG. 8, the same reference numerals as in FIG. 4 are used for components equivalent to those shown in FIG. 4, only those necessary for the description here, and the duplicated description of those components will be omitted below. FIG. 7(A) shows the first modified example, FIG. 7(B) shows the second modified example, and FIG. 7(C) shows the third modified example. FIG. 8(A) shows the fourth modified example, FIG. 8(B) shows the fifth modified example, and FIG. 8(C) shows the sixth modified example.

[0047] 4, the ratio of the thickness T of the cylindrical wall 123b to the thickness t of the cylindrical wall 111 in the valve body 11 is T=0.95t, which satisfies the relationship in the above-mentioned (Formula 3). In addition, the ratio of the length L of the axial direction D11 to the thickness T of the cylindrical wall 123b in the impact stress relaxation portion 123 is L=1.2T, which satisfies the relationship in the above-mentioned (Formula 1).

[0048] Next, in the impact stress mitigating parts 123-1, 123-2, and 123-3 of the first to third modified examples shown in Fig. 7, the ratio of the thickness T of the cylindrical walls 123-1b, 123-2b, and 123-3b to the thickness t of the cylindrical wall 111 in the valve body 11 is T = 1t. Similarly, in the impact stress mitigating parts 123-4 and 123-6 of the fourth and sixth modified examples shown in Fig. 8, the ratio of the thickness T of the cylindrical walls 123-4b and 123-6b to the thickness t of the cylindrical wall 111 in the valve body 11 is T = 1t. On the other hand, in the impact stress mitigating part 123-5 of the fifth modified example, since a small diameter recess 123-5c described later is formed, the ratio of the thickness T of the cylindrical wall 123-5b to the thickness t of the cylindrical wall 111 in the valve body 11 is T = 0.5t. Similar to the impact stress absorbing portion 123 shown in FIG. 4, these ratios also satisfy the relationship of the above-mentioned (Equation 3).

[0049] In the impact stress mitigation portion 123-1 of the first modification shown in FIG. 7(A), the ratio of the length L in the axial direction D11 to the thickness T of the cylindrical wall 123-1b is L=0.5T. In the impact stress mitigation portion 123-2 of the second modification shown in FIG. 7(B), L=1T, and in the impact stress mitigation portion 123-3 of the third modification shown in FIG. 7(C), L=2T. All of these three types of ratios satisfy the relationship of the above-mentioned (Formula 1), as in the impact stress mitigation portion 123 shown in FIG. 4. In the impact stress mitigation portion 123-4 of the fourth modification shown in FIG. 8(A), L=2.5T, and in the impact stress mitigation portion 123-6 of the sixth modification shown in FIG. 8(C), L=5T. These three types of ratios also satisfy the relationship of the above-mentioned (Formula 1). If this ratio deviates from the above-mentioned relationship in (Formula 2) and becomes L>5T, the increase in size in the axial direction D11 of the cover member including the impact stress absorbing part becomes noticeable. The relationship in (Formula 2) above, L≦5T, is an upper limit regulation for preventing the increase in size in the axial direction D11 of the impact stress absorbing part.

[0050] Further, the impact stress absorbing portion 123 of the embodiment shown in Fig. 4 and the impact stress absorbing portions 123-1, 123-2, 123-3 of the first to third modified examples shown in Fig. 7 are all provided with a small diameter cylindrical protrusion 123c as follows. Note that since this small diameter cylindrical protrusion is an equivalent portion in the embodiment of Fig. 4 and the first to third modified examples of Fig. 7, the same reference numeral "123c" is used in Figs. 4 and 7.

[0051] The small diameter cylindrical protrusion 123c is a portion that protrudes in a cylindrical shape in the axial direction D11 from a position close to the inner periphery of the protruding end edge 123a of the impact stress mitigating portion 123,...,123-3 toward the opening 11a of the valve body 11. The small diameter cylindrical protrusion 123c has a diameter smaller than the outer diameter of the impact stress mitigating portion 123,...,123-3. On the other hand, the opening end 11b of the valve body 11 is provided with a positioning recess 11c, into which the small diameter cylindrical protrusion 123c is fitted at a position close to the inner periphery of the opening end 11b, for positioning the cover member 12 when it is attached.

[0052] In the present embodiment and the first to third modified examples, the fixed portion between the valve body 11 and the cover member 12 is the welded portion 16 formed by welding as described above. The welded portion 16 is formed so that the welded depth Dp does not penetrate the small diameter cylindrical projection 123c in the thickness direction D13.

[0053] Moreover, unlike the above-described embodiment and the first to third modified examples, the impact stress absorbing portions 123-4, 123-5, and 123-6 of the fourth to sixth modified examples shown in FIG. 8 are provided with the following small diameter recesses 123-4c, 123-5c, and 123-6c.

[0054] The small diameter recesses 123-4c, 123-5c, 123-6c are recessed from an inner peripheral position of the protruding end edge 123a of the impact stress absorbing portions 123-4, 123-5, 123-6 in the axial direction D11 toward the stopper portion 122 to a diameter smaller than the outer diameter of the impact stress absorbing portions 123-4, 123-5, 123-6. On the other hand, the opening end 11b of the valve body 11 is provided with positioning protrusions 11-4c, 11-5c, 11-6c at a position closer to the inner peripheral position of the opening end 11b, which are fitted into the small diameter recesses 123-4c, 123-5c, 123-6c to position the cover member 12 when it is attached.

[0055] In the fourth to sixth modified examples, the small diameter recesses 123-4c, 123-5c, and 123-6c have different lengths in the axial direction D11. In the fifth modified example, the small diameter recess 123-5c is formed in the axial direction D11 until it reaches the outer circumferential edge 122b of the stopper portion 122, that is, over the entire length of the impact stress mitigation portion 123-5. As a result, as described above, the impact stress mitigation portion 123-5 in the fifth modified example is thin such that the ratio of the thickness T of the cylindrical wall 123-5b to the thickness t of the cylindrical wall 111 in the valve body 11 is T=0.5t. In the fourth and sixth modified examples, the positioning protrusions 11-4c, 11-5c, and 11-6c protrude by a length corresponding to the length in the axial direction D11 of the small diameter recesses 123-4c and 123-6c into which the positioning protrusions 11-4c and 11-6c are fitted. In the fifth modified example, the positioning protrusion 11-5c has substantially the same length as the positioning protrusion 11-4c in the fourth modified example, and is fitted into the small diameter recess 123-5c halfway toward the opening. In the fourth to sixth modified examples, by providing such positioning protrusions 11-4c, 11-5c, and 11-6c in the valve body 11, the piston 221 is configured to stay inside the valve body 11 when it abuts against the stopper portion 122, while the length L of the impact stress mitigation portions 123-4, 123-5, and 123-6 can be made longer, such as 2T to 5T, compared to the first to third modified examples, so that the stress generated in the welded portion 16 due to the impact when the piston 221 abuts against the stopper portion 122 is further mitigated.

[0056] In addition, in the fourth to sixth modified examples, the welded portion 16, which serves as a fixing portion between the valve body 11 and the cover member 12, is formed so that its weld depth Dp is a depth that does not penetrate the above-mentioned positioning protrusions 11-4c, 11-5c, and 11-6c in the thickness direction D13.

[0057] According to the slide type switching valve 10 and the refrigeration cycle system 30 of the embodiment and the first to sixth modified examples described above, the following effects can be obtained. That is, in the embodiment and the first to sixth modified examples, first, the impact stress mitigation means (1) (arrangement of the impact stress mitigation part) is adopted as the impact stress mitigation means for mitigating the stress generated by the impact when the piston 221 abuts against the stopper part 122 in the cover member 12.

[0058] The impact stress mitigation means (1) (disposition of the impact stress mitigation portion) is a means in which impact stress mitigation portions 123, . . . , 123-6 are provided between the stopper portion 122 and the opening end 11b of the valve body 11, protruding from the outer peripheral edge 122b of the stopper portion 122 in the axial direction D11, and the protruding end edge 123a is abutted against the opening end 11b of the valve body 11 and fixed to the opening end 11b. With this, when the piston 221 abuts against the stopper portion 122 with a large collision load due to the use of an ultra-high pressure fluid in the refrigeration cycle system, the stopper portion 122 receives the collision load at a position away from the welded portion 16 between the valve body 11 and the cover member 12 to the outside in the axial direction D11 of the valve body 11. Therefore, the collision load is less likely to directly act on the welded portion 16 as a stress that tries to peel them apart, and therefore durability against the collision load when the piston 221 abuts against the stopper portion 122 of the cover member 12 can be improved.

[0059] Next, the impact stress relaxation means (2) (flexural deformation) is a means for mitigating stress generated in the welded portion 16 by the impact of the piston 221 when the operating conditions become high-load operating conditions, the high-low pressure difference becomes large, and the collision load when the piston 221 abuts against the stopper portion 122 becomes excessively large, by the stopper portion 122 being flexibly deformed in the axial direction D11 within its elastic range, and the impact stress relaxation portions 123, . . . , 123-6 being flexibly deformed in the transverse direction D12 to the axial direction D11 within their elastic range. In other words, even with the impact stress relaxation means (2) (flexural deformation), the collision load at the time of abutment is less likely to act as a stress that tries to separate the open end 11b of the valve body 11 and the welded portion 16 of the lid member 12 from each other. As a result, durability against the collision load when the piston 221 abuts against the stopper portion 122 of the lid member 12 can be improved.

[0060] Here, in this embodiment and the first to sixth modified examples, the impact stress mitigating portions 123,...,123-3 are formed so that the length L in the axial direction D11 and the thickness T of the cylindrical walls 123b,...,123-3b satisfy the relationship of 0.5T≦L. With this configuration, the length L in the axial direction D11 of the impact stress mitigating portions 123,...,123-6 is made sufficiently long, and the stopper portion 122 is disposed at a position sufficiently away from the welded portion 16 between the valve body 11 and the lid member 12 on the outer side in the axial direction D11 of the valve body 11. With this arrangement, the stress at the welded portion 16 can be more effectively mitigated.

[0061] Furthermore, in this embodiment and the first to sixth modified examples, the impact stress mitigating portions 123,...,123-6 are formed so as to further satisfy the relationship L≦5T. With this configuration, it is possible to effectively mitigate stress while preventing the cover member 12 including the impact stress mitigating portions 123,...,123-6, that is, the slide type switching valve 10, from becoming large.

[0062] In the present embodiment and the first to third modified examples, the impact stress mitigating portions 123,...,123-3 are provided with small diameter cylindrical protrusions 123c, and the opening end 11b of the valve body 11 is provided with positioning recesses 11c. In the fourth to sixth modified examples, the impact stress mitigating portions 123-4, 123-5,123-6 are provided with small diameter recesses 123-4c, 123-5c,123-6c, and the opening end 11b of the valve body 11 is provided with positioning protrusions 11-4c, 11-5c,11-6c. According to these configurations, the cover member 12 is positioned with respect to the opening 11a of the valve body 11 by fitting the small diameter cylindrical protrusion 123c into the positioning recess 11c, or by fitting the positioning protrusions 11-4c, 11-5c, and 11-6c into the small diameter recesses 123-4c, 123-5c, and 123-6c, so that the subsequent fixing work can be performed with good workability.

[0063] In the present embodiment and the first to sixth modified examples, the fixed portion between the valve body 11 and the cover member 12 is the welded portion 16, and this welded portion 16 is formed with a weld depth Dp that does not penetrate the small diameter cylindrical protrusion 123c or the positioning protrusions 11-4c, 11-5c, 11-6c in the thickness direction D13. According to this configuration, the welded portion 16 as the fixed portion does not penetrate the small diameter cylindrical protrusion 123c or the positioning protrusions 11-4c, 11-5c, 11-6c of the cover member 12, so that it is possible to effectively prevent the intrusion of spatter into the inside of the valve body 11 during welding.

[0064] The above-described embodiment and the first to sixth modified examples merely show typical forms of the present invention, and the present invention is not limited thereto. In other words, the present invention can be embodied in various modifications without departing from the gist of the present invention. As long as such modifications still include the configuration of the slide type switching valve and the refrigeration cycle system of the present invention, they are of course included in the scope of the present invention.

[0065] For example, in the above-mentioned embodiment and the first to sixth modified examples, the slide type switching valve 10 is exemplified as a four-way switching valve that switches the communication state of four pipes as an example of the slide type switching valve, but the slide type switching valve is not limited to the four-way switching valve. The slide type switching valve may be a three-way switching valve that uses a slide valve body to switch the pipes to be communicated when communicating a pair of pipes out of three pipes, as long as at least a pair of pipes is connected to a valve housing. Alternatively, it may be a two-way switching valve that uses a slide valve body to open and close between two pipes. The number of pipes in the slide type switching valve, the method of switching the communication state, and the like can be appropriately set depending on the application target of the slide type switching valve, and the like.

[0066] Furthermore, in the above-described embodiment and the first to sixth modified examples, a valve housing 1 in which openings 11a at both ends of a cylindrical valve body 11 are closed with a lid member 12 having a lid body portion 121 formed into a dome-shaped covered cylindrical shape is exemplified as an example of a valve housing. However, the valve housing is not limited to this, and the valve body may be a tubular shape other than a cylindrical shape, and the lid body portion of the lid member may also be a covered tubular shape other than a dome-shaped covered cylindrical shape as long as it closes the opening of the valve body.

[0067] In addition, in the above-mentioned embodiment and the first to sixth modified examples, the impact stress mitigating parts 123,...,123-6 in which the thickness T of the cylindrical wall 123b and the thickness t of the cylindrical wall 111 in the valve body 11 satisfy the relationship of 0.5t≦T≦1.5t are exemplified as an example of the impact stress mitigating part. However, the impact stress mitigating part is not limited to this, and may be formed so as to deviate from this relationship. However, as described above, the relationship of 0.5t≦T≦1.5t is a preferable relationship in terms of the stress mitigating effect at the welded part 16. Note that, in the embodiment and the first to sixth modified examples, the impact stress mitigating part 123 in which T=0.95t and the impact stress mitigating parts 123-1,...,123-6 in which T=1t are exemplified as specific examples that satisfy this relationship. However, the impact stress mitigating part in the case where the relationship of 0.5t≦T≦1.5t is satisfied is not limited to this, and any thickness that satisfies the above relationship may be adopted as the thickness of the cylindrical wall.

[0068] In addition, in the above-mentioned embodiment and the first to sixth modified examples, the impact stress mitigating parts 123,...,123-6 in which the length L in the axial direction D11 and the thickness T of the cylindrical wall 123b,...,123-6b satisfy the relationship of 0.5T≦L are exemplified as an example of the impact stress mitigating part. However, the impact stress mitigating part is not limited to this, and may be formed so that the axial length is 0.5T>L. However, as described above, the impact stress mitigating parts 123,...,123-6 formed so as to satisfy the relationship of 0.5T≦L are easily bent and can more effectively mitigate the stress at the welded part 16. Note that, in the embodiment and the first to sixth modified examples, the impact stress mitigating part 123 with L=1.2T and the impact stress mitigating parts 123-1,...,123-6 with L=0.5T, 1T, 2T, 2.5T, 5T are exemplified as specific examples that satisfy this relationship. However, the impact stress absorbing portion in the case where the relationship 0.5T≦L is satisfied is not limited to this, and any thickness that satisfies the above relationship may be adopted as the thickness of the cylindrical wall.

[0069] In the above-described embodiment and the first to sixth modified examples, the impact stress mitigating parts 123,...,123-6 that satisfy the relationship L < 5T in addition to the relationship 0.5T < L are exemplified as an example of the impact stress mitigating part. However, the impact stress mitigating part is not limited to this, and may be formed so as to satisfy the relationship 0.5T < L but to satisfy L > 5T. However, as described above, according to the impact stress mitigating parts 123,...,123-6 formed so as to satisfy the relationship L < 5T, it is possible to suppress the size of the slide type switching valve 10 from increasing. Note that, in the embodiment and the first to sixth modified examples, the impact stress mitigating part 123 that satisfies L = 1.2T and the impact stress mitigating parts 123-1,...,123-6 that satisfies L = 0.5T, 1T, 2T, 2.5T, 5T are exemplified as specific examples that satisfy this relationship. However, the impact stress absorbing portion in the case where the relationship L≦5T is satisfied is not limited to this, and any thickness that satisfies the above relationship may be adopted as the thickness of the cylindrical wall.

[0070] In the above-described embodiment and the first to sixth modified examples, the impact stress mitigating portion and the valve body are exemplified by the impact stress mitigating portion 123,...,123-6 provided with the small diameter cylindrical protrusion 123c or the small diameter recessed portion 123-4c, 123-5c, 123-6c, and the valve body 11 provided with the positioning recess 11c or the positioning protrusion 11-4c, 11-5c, 11-6c. However, the impact stress mitigating portion and the valve body are not limited thereto, and may be one not provided with the small diameter cylindrical protrusion, the small diameter recess, the positioning recess, or the positioning protrusion. However, as mentioned above, by providing the small diameter cylindrical protrusions 123c, the small diameter recesses 123-4c, 123-5c, 123-6c, the positioning recesses 11c, and the positioning protrusions 11-4c, 11-5c, 11-6c on the impact stress absorbing portions 123, ..., 123-6 and the valve body 11, the fixing operation of the cover member 12 to the opening 11a of the valve body 11 can be performed with good workability.

[0071] In the above-described embodiment and the first to third modified examples, the valve housing 1 is exemplified as an example of the valve housing, in which the valve body 11 and the cover member 12 are fixed by forming a welded portion 16 having a weld depth Dp that does not penetrate the small diameter cylindrical protrusion 123c or the positioning protrusions 11-4c, 11-5c, and 11-6c. However, the valve housing is not limited to this, and the cover member may be fixed to the valve body by a welded portion formed with a weld depth that penetrates the small diameter cylindrical protrusion or the positioning protrusion. However, as described above, by forming the welded portion 16 with a weld depth Dp that does not penetrate the small diameter cylindrical protrusion 123c or the positioning protrusions 11-4c, 11-5c, and 11-6c, it is possible to effectively prevent the intrusion of spatters into the inside of the valve body 11 during welding. [Explanation of symbols]

[0072] 1 Valve housing 1A Hyperbaric Chamber 1B First working chamber 1C Second working chamber 2 Slide valve body 3 Pilot valve 10. Slide type switching valve 11 Valve body 11a opening 11b Open end 11c Positioning recess 11-4c, 11-5c, 11-6c Positioning protrusions 12 Lid member 13c C joint pipe 13d D joint pipe 13e E joint pipe 13s S joint pipe 14L Thin tube for first housing 14R Thin tube for second housing 16 Welded parts 21 Valve body 21A Bowl-shaped recess 22 Slide mechanism 30 Refrigeration Cycle System 31 Compressor 32 Outdoor heat exchanger 33 Indoor heat exchanger 34 Squeezing device 121 Lid body part 121a Cylinder opening 121b Opening edge 121c Mounting hole 122 Stopper part 122a Stopper surface 122b Outer rim 123, 123-1, 123-2, 123-3, 123-4, 123-5, 123-6 Impact stress relief section 123a Protruding edge 123b,123-1b,123-2b,123-3b,123-4b,123-5b,123-6b Cylinder wall 123c Small diameter cylindrical protrusion 123-4c, 123-5c, 123-6c Small diameter recess 221 Piston 222 Connecting plate 222a Through hole D11 Axial direction D12 Cross direction D13 Thickness direction Dp Weld depth F11, F12, F13, F14, F15 Stress ratio change curve G Graph T: Wall thickness at impact stress relief section t Thickness of the valve wall L Axial length in impact stress relief section X axis φ11 Inner diameter of valve body opening φ12 Outer diameter of the lid body φ13 Inner diameter of stopper φ14 Outer diameter of valve body

Claims

1. a valve housing having a cylindrical shape and including a valve body having at least one pair of pipes connected to its peripheral wall, the openings at both ends of the valve body being closed by cover members; a valve body that is slidably installed in the valve body in an axial direction of the valve body and switches a communication state of the pipe; a slide mechanism which is a mechanical part extending in the axial direction inside the valve body and having pistons at both ends, the slide mechanism having the valve body connected to an intermediate part thereof and receiving a slide driving force in the axial direction by the pistons to slide the valve body, The cover member is a lid body portion formed in a covered cylindrical shape having an inner diameter smaller than an inner diameter of the opening of the valve body, the lid body portion being disposed outside the opening of the valve body in the axial direction so that the cylindrical opening faces the opening of the valve body; a stopper portion that projects from an opening edge of the cylinder opening of the lid main body portion toward the outside of the lid main body portion in a flange-like shape having an outer diameter larger than the inner diameter of the opening of the valve body, and a surface facing the opening abuts against and receives the piston on one end side of the slide mechanism that has slid through the opening in the axial direction; and an impact stress relief means for relieving stress caused by an impact when the piston abuts against the stopper portion, a valve body having an opening end surrounding the opening of the valve body, the opening end being provided with an outer peripheral edge of the stopper portion and having a cylindrical shape protruding in the axial direction from the outer peripheral edge of the stopper portion, the protruding edge of which abuts against the opening end of the valve body and is fixed to the opening end, thereby relieving the stress.

2. 2. The slide type switching valve according to claim 1, characterized in that the impact stress absorbing means, in addition to providing the impact stress absorbing portion, also serves as a means for absorbing the stress by causing the stopper portion to flex and deform in the axial direction and the impact stress absorbing portion to flex and deform in a direction perpendicular to the axial direction due to the impact when the stopper portion contacts the piston.

3. When the length in the axial direction of the cylindrical impact stress absorbing portion is L and the thickness of the cylindrical wall is T, 0.5T≦L 2. The slide type switching valve according to claim 1, characterized in that the slide type switching valve is formed so as to satisfy the relationship:

4. The impact stress absorbing portion further comprises: L≦5T 4. The slide type switching valve according to claim 3, wherein the slide type switching valve is formed so as to satisfy the relationship:

5. the impact stress absorbing portion is provided with a small-diameter cylindrical protrusion that protrudes in the axial direction from a position near the inner periphery of the protruding end edge toward the opening side of the valve body and has a cylindrical shape with a diameter smaller than an outer diameter of the impact stress absorbing portion, or a small-diameter recess that recesses in the axial direction from a position near the inner periphery of the protruding end edge toward the stopper portion and has a diameter smaller than the outer diameter of the impact stress absorbing portion, 2. The slide type switching valve according to claim 1, characterized in that the opening end of the valve body is provided with a positioning recess, at a position toward the inner circumference of the opening end, into which the small diameter cylindrical protrusion of the impact stress absorbing portion is fitted to position the cover member when it is attached, or a positioning convex portion, at a position toward the inner circumference of the opening end, which is fitted into the small diameter recess of the impact stress absorbing portion to position the cover member when it is attached.

6. 6. The slide type switching valve according to claim 5, characterized in that the fixed portion is a welded portion formed by welding the protruding end edge to the opening end of the valve body from the outer peripheral surface side of the valve body, and is formed with a welding depth that does not penetrate the small diameter cylindrical protrusion or the positioning convex portion in the thickness direction.

7. A refrigeration cycle system comprising: a compressor that compresses a refrigerant which is a fluid; a first heat exchanger that functions as a condenser in a cooling mode; a second heat exchanger that functions as an evaporator in the cooling mode; an expansion means that expands and reduces the pressure of the refrigerant between the first heat exchanger and the second heat exchanger; and the slide-type switching valve according to any one of claims 1 to 6.

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