Valve device and refrigeration cycle system

Abstract

To provide a valve device which is less affected by temperature change and can stably maintain sealing performance, and to provide a refrigeration cycle system.SOLUTION: A piston 50 of a cylindrical guide part 10 of a valve device is provided with a seal part 70 that partitions a space inside the guide part 10 into a plurality of spaces. The seal part 70 is provided with an L packing 80 and a leaf spring 90. The leaf spring 90 is provided with: a plate-shaped substrate part 91; and a plurality of blade parts 92 that rises from the substrate part 91 and press a rim part 82 of the L packing 80 against the guide part 10 by pressing the rim part 82 from the inner surface side to the outer surface side. The blade part 92 is provided with a first bent part 93 (bent part), a first blade part 94 (plate part), and a second bent part 95 (end edge part). A width dimension of the first blade part 94 decreases or remains the same from the first bent part 93 side toward the second bent part 95 side.SELECTED DRAWING: Figure 9

Description

[Technical Field]

[0001] The present invention relates to a valve device and a refrigeration cycle system. [Background technology]

[0002] A valve device for controlling the flow of a fluid is known (see, for example, Patent Document 1). The valve device described in Patent Document 1 includes a seal portion 4 for preventing fluid leakage, as shown in FIG. 2 of Patent Document 1. The seal portion 4 is disposed within a cylindrical guide portion 21 and divides the space within the guide portion 21 into one side in the direction of the axis X and the other side in the direction of the axis X. The seal portion 4 includes an L-shaped packing 45 including an annular base portion 45a and a rim portion 45b erected on the outer peripheral edge of the base portion 45a. A leaf spring 41 is stacked on the inner surface of the L-shaped packing 45. The leaf spring 41 includes a disk-shaped base portion 41a disposed on the inner surface of the base portion 45a, and blade portions 41b that rise from the base portion 41a and elastically deform in the thickness direction. As shown in FIG. 3 of Patent Document 1, both widthwise ends of the blade portions 41b at the tip side form an end point P with the rim portion 45b. End point P presses rim portion 45b outward by spring force, which is the repulsive force after elastic deformation of blade portion 41b, and rim portion 45b is tightly attached to the inner surface of guide portion 21 by the tension of the pressed rim portion 45b. [Prior art documents] [Patent documents]

[0003] [Patent Document 1] Japanese Patent Application Publication No. 2017-223293 Summary of the Invention [Problem to be solved by the invention]

[0004] As shown in FIG. 3 of Patent Document 1, the seal portion 4 described in Patent Document 1 has the blades 41b wider at the tip end than at the base end (i.e., the width of the blades 41b at the base end is narrower). Therefore, to provide a sufficient number of blades 41b to ensure sealing performance, the gaps 41c between the blades 41b must be narrower than the width of the blades 41b at the tip end. This results in the multiple end points P being unevenly spaced along the circumference of the base portion 41a. This can result in insufficient pressure being applied to a portion of the rim portion 45b, causing the rim portion 45b to lift, resulting in an unstable contact state and potentially affecting sealing performance. While it might be possible to narrow the width of the blades 41b to even out the spacing between the end points P, this would further reduce the width of the blades 41b at the base end, potentially reducing the strength of the leaf spring 41. This is particularly undesirable when the temperature of the operating environment is prone to change, such as due to temperature changes in the fluid or the outside of the valve device. Specifically, when the temperature of the seal portion 4 drops, the L-shaped packing 45 contracts, causing the rim portion 45b to press the blade portion 41b in a direction away from the inner surface of the guide portion 21, which can apply a load to the tip side of the leaf spring 41. In this case, the width dimension of the blade portion 41b is smaller at the base side, where greater stress is generated than at the tip side, and the strength of the base side is likely to be insufficient. This makes it difficult to increase the design load of the entire leaf spring 41. This makes it difficult to maintain the tension of the rim portion 45b and maintain the sealing performance of the seal portion 4.

[0005] An object of the present invention is to provide a valve device and a refrigeration cycle system that are less susceptible to temperature changes and can stably maintain sealing performance. [Means for solving the problem]

[0006] In order to solve the above problems and achieve the object, the valve device of the present invention is a valve device comprising a cylindrical guide portion, a moving member that moves along the axis of the guide portion, and a valve body that is connected to the moving member and controls the flow of a fluid, wherein the moving member is provided with a seal portion that divides the space within the guide portion into a plurality of spaces, the seal portion comprising an L-shaped packing that fits into the inner surface of the guide portion, and a leaf spring that acts on the L-shaped packing, and the L-shaped packing comprises a plate-shaped base portion that extends intersecting the axis, and a rim portion that rises from the edge of the base and slides against the inner surface of the guide portion. The leaf spring comprises a plate-shaped substrate portion arranged on the inner surface side of the base portion, and a plurality of blade portions which are provided so as to protrude radially from the substrate portion around the axis and which press the rim portion from the inner surface side to the outer surface side, thereby pressing the rim portion against the guide portion, and the blade portions comprise a bent portion which forms the boundary with the substrate portion, a plate portion which rises from the bent portion, and an edge portion which is provided on the tip side of the plate portion and abuts the rim portion, and the width dimension of the plate portion becomes smaller or remains constant as it moves from the bent portion side to the edge portion side.

[0007] According to the present invention, the width of the plate portion decreases or remains constant from the bent portion side toward the edge portion side, making it easier to reduce the width of the edge portion abutting the rim portion. This facilitates uniformly arranging the edge portion in the circumferential direction around the axis. This prevents localized insufficient pressure on the rim portion, thereby maintaining stable sealing performance by the seal portion. Furthermore, with this configuration, the width of the plate portion is larger or uniform on the bent portion side than on the edge portion side. This facilitates ensuring the required strength on the bent portion side (the base side of the blade portion) where greater stress occurs when a load is applied from the rim portion to the blade portion via the edge portion, and allows the multiple blade portions to optimally bear the load. This allows the design load of the entire leaf spring to be increased, and the tension of the rim portion can be stably maintained even in environments where the seal portion expands or contracts due to temperature changes, etc. Therefore, a valve device can be provided that is less susceptible to temperature changes and can maintain stable sealing performance.

[0008] In this case, it is preferable that both widthwise ends of the plate portion have straight portions that connect the bent portions and the edge portions. With this configuration, no special processing is required for both widthwise ends of the plate portion, and the shape of the plate portion can be simplified, which reduces mold manufacturing costs and makes it possible to manufacture the seal portion at low cost.

[0009] Furthermore, both widthwise ends of the plate portion may include a tapered portion inclined toward each other toward the edge portion, and a straight portion continuous with the edge portion of the tapered portion and extending toward the edge portion, so that the portions are parallel to each other. With this configuration, the width of the blade is smaller on the straight portion side than on the tapered portion side, making it easier to reduce the width of the edge portion that abuts the rim portion. This facilitates circumferentially uniformly arranging the edge portions around the axis. Furthermore, with this configuration, the width of the blade is larger on the tapered portion side than on the straight portion side. This makes it easier to ensure the strength required on the tapered portion side (the base side of the blade), where greater stress occurs when a load is applied to the blade from the rim portion via the edge portion, and allows the multiple blades to favorably bear the load. This allows the design load of the entire leaf spring to be increased, and the tension of the rim portion can be stably maintained even in environments where the seal portion expands or contracts due to temperature changes, etc.

[0010] Furthermore, both widthwise ends of the plate portion may have curved portions that converge toward the edge portion. With this configuration, the width of the blade is smaller on the edge portion side than on the bent portion side of the curved portion, making it easier to reduce the width of the edge portion that abuts the rim portion. This facilitates uniformly arranging the edge portions in the circumferential direction around the axis. Furthermore, with this configuration, the width of the blade is larger on the bent portion side than on the edge portion side of the curved portion. This facilitates ensuring the required strength at the bent portion side (the base side of the blade), where greater stress occurs when a load is applied to the blade from the rim portion via the edge portion, and allows the multiple blades to optimally bear the load. This allows for a larger design load for the entire leaf spring, and the tension of the rim portion can be stably maintained even in environments where the seal portion expands or contracts due to temperature changes, etc.

[0011] Furthermore, the edge of the base member has an arc portion connecting the bent portions of adjacent blades. The arc portion is formed in a convex arc shape opposite the protruding direction of the blades, and preferably satisfies the relationship t≦R≦5t, where R is the radius of the arc portion and t is the thickness of the blades. This configuration allows the radius of the arc portion to be limited to a maximum of approximately five times the thickness of the blades, making it easier to position adjacent blades relatively close to each other. This increases the number of blades that can be formed per perimeter of the base member, distributes the load applied to the blades, and more stably maintains the state in which the blades press against the rim portion. While a too small radius of the arc portion increases the management costs of the mold used to form the leaf spring, this configuration prevents the radius of the arc portion from becoming too small by making it equal to or greater than the thickness of the blades, thereby keeping the management costs of the mold reasonable.

[0012] Furthermore, each of the widthwise ends of the blade is provided with abutment portions that abut against the rim portion. The abutment portions preferably have a predetermined length from the edge toward the bent portion and are inclined toward each other or parallel toward the protruding side of the blade. With this configuration, the abutment portions have a predetermined length from the edge toward the bent portion and are inclined toward each other or parallel toward the protruding side of the blade. This increases the contact area between the blade and the rim portion, thereby improving the sealing performance of the seal, as described below. That is, when comparing seal members having the same circumferential length of the base plate, the same number of blades, and the same circumferential length of the rim portion, the width dimension of the edge portion of this configuration (the second bent portion of the conventional configuration) is smaller than a configuration in which the abutment portions are inclined toward the protruding side of the blade (for example, blade portion 41b shown in FIG. 3 of Patent Document 1, hereinafter referred to as the conventional configuration). This makes it easier to suppress deformation between both widthwise ends of the edge portion (second bent portion) when force is applied between the abutment portions, compared to conventional configurations, and allows the abutment portion to abut the rim portion reliably. Furthermore, with this configuration, for example, if the rim portion is made of a material such as resin that is easily deformed, deformation of the edge portion is suppressed as described above, and the edge portion abuts the rim portion reliably, allowing the edge portion to sink deeply into the rim portion and make contact as a linear surface. Therefore, as described above, the contact area between the blade portion and the rim portion can be increased, improving the sealing performance of the seal portion.

[0013] Furthermore, it is preferable that the rim portion be configured with n blades, and that 2n abutment portions be arranged at equal intervals in the circumferential direction around the axis, thereby pressing the rim portion from the inner surface side to the outer surface side. With this configuration, by uniformly arranging the abutment portions in the circumferential direction in a number twice the number of blades, the uniform gap between the abutment portions can be made smaller than in a configuration in which the rim portion is pressed at a single point on the blade, and the shape when multiple abutment portions are connected can be made closer to a regular polygon. As a result, the pressure on the rim portion is less likely to be locally insufficient, and the rim portion can be further prevented from lifting off the inner surface of the guide portion.

[0014] Furthermore, the blades are provided with second plate portions extending from the edge portions toward the inside of the leaf spring, and the abutment portions preferably have a predetermined length spanning the edge portions and are inclined toward each other or parallel toward the protruding side of the blades. According to this configuration, the abutment portions have a predetermined length spanning the edge portions and are inclined toward each other or parallel toward the protruding side of the blades. This configuration reduces the width of the edge portions (second bent portions in the conventional configuration) compared to the conventional configuration. This makes it easier to suppress deformation between the widthwise ends of the edge portions (second bent portions) when force is applied between the abutment portions compared to the conventional configuration, allowing the abutment portions to reliably abut against the rim portion. Furthermore, with this configuration, for example, when the rim portion is made of a material such as a deformable resin, deformation of the edge portions is suppressed and they reliably abut against the rim portion, allowing the edge portions to sink deeply into the rim portion and make contact as a linear surface. Therefore, as described above, the contact area between the blade portion and the rim portion can be increased, and the sealing performance of the seal portion can be improved.

[0015] The valve device of the present invention is a valve device comprising a cylindrical guide portion, a moving member that moves along the axis of the guide portion, and a valve body that is connected to the moving member and controls the flow of a fluid, wherein the moving member is provided with a seal portion that divides the space within the guide portion into a plurality of spaces, the seal portion comprises an L-shaped packing that fits into the inner surface of the guide portion, and a leaf spring that acts on the L-shaped packing, the L-shaped packing having a plate-shaped base that extends intersecting the axis, and a rim that rises from the edge of the base and comes into sliding contact with the inner surface of the guide portion, and the leaf spring is disposed on the inner surface side of the base. and a plurality of blade portions which are provided so as to protrude radially from the base portion around the axis and which press the rim portion from the inner surface side to the outer surface side, thereby pressing the rim portion against the guide portion, wherein the blade portions have a bent portion which forms the boundary with the base portion, a plate portion which rises from the bent portion, and an edge portion which is provided on the tip side of the plate portion and abuts against the rim portion, and both widthwise ends on the outer surface side of the edge portion and an edge portion which connects the both widthwise ends form abutment portions which abut against the rim portion, and the curvature of the edge portion is approximately the same as the curvature of the inner surface of the rim portion.

[0016] In a configuration in which both widthwise ends of the second bent portion are pressed against the rim portion, the pressing force against the rim portion between the ends may be insufficient. For example, in a blade portion such as the leaf spring described in Patent Document 1, the tip side is formed wider than the base side, which tends to result in a wide gap between the contact portions of one blade portion. This tends to result in particularly insufficient pressing force of the rim portion between the contact portions of one blade portion. Therefore, for example, if the rim portion contracts (thermally deforms) due to a drop in temperature, the rim portion may lift up toward the blade portion between the ends of the second bent portion, potentially resulting in fluid leakage. In response to this issue, the leaf spring of this configuration has an edge portion with a curvature set to approximately the same curvature as the inner surface of the rim portion as well as the widthwise ends of the blade portion as the contact portion. This allows the contact area between the blade portion and the rim portion for each blade portion to be efficiently and uniformly increased between the widthwise ends of the blade portion, thereby effectively suppressing lifting of the rim portion. Therefore, it is possible to provide a valve device that is less susceptible to temperature changes and can stably maintain sealing performance.

[0017] The present invention also provides a refrigeration cycle system including a slide-type switching valve, the slide-type switching valve being configured using any of the valve devices described above. With this configuration, it is possible to provide a refrigeration cycle system that is less susceptible to temperature changes and can stably maintain sealing performance. [Effects of the Invention]

[0018] According to the present invention, it is possible to provide a valve device and a refrigeration cycle system that are less susceptible to temperature changes and can stably maintain sealing performance. [Brief explanation of the drawings]

[0019] [Figure 1] 1 is a cross-sectional view of a motor-operated valve according to a first embodiment of the present invention, taken along the axial direction of a guide portion. [Figure 2] FIG. 2 is an enlarged cross-sectional view of a portion of region A in FIG. 1. [Figure 3]1A is a cross-sectional view showing the state of the L-shaped packing that constitutes the sealing portion before deformation, and FIG. 1B is a cross-sectional view showing the state of the L-shaped packing after deformation. [Figure 4] (A) is a perspective view of a leaf spring, and (B) is a front view of the leaf spring with the blades unfolded. [Figure 5] 1A is a perspective view of a blade portion that constitutes a part of a leaf spring, and FIG. 1B is a cross-sectional view of the blade portion cut along the longitudinal direction. [Figure 6] FIG. 10 is an enlarged front view of a portion of the leaf spring with the blades deployed. [Figure 7] FIG. 7 is an enlarged front view of the blade portion shown in FIG. 6. [Figure 8] 4A is a cross-sectional view showing a state before deformation of a leaf spring that constitutes a sealing portion, and FIG. 4B is a cross-sectional view showing a state after deformation of the leaf spring. [Figure 9] 1A is a cross-sectional view of a guide part to which a leaf spring is attached, cut in a direction perpendicular to the axis of the guide part, and FIG. 1B is a front view showing the dimensional relationship of the leaf spring. [Figure 10] 1 is a conceptual diagram showing a refrigeration cycle system of the present invention. [Figure 11] 11(A) is a perspective view of a leaf spring according to a modified example of the first embodiment, FIG. 11(B) is a front view showing the dimensional relationship of a leaf spring having the wing portion shown in FIG. 11(A), and FIG. 11(C) is a front view of the leaf spring with the wing portion shown in FIG. 11(A) unfolded. [Figure 12] (A) and (B) are cross-sectional views showing variations of leaf springs. [Figure 13] 13(A) is a front view of a leaf spring with blade portions unfolded in the second embodiment, and FIG. 13(B) is an enlarged front view of a main part of FIG. 13(A). [Figure 14] 14(A) is a front view of a leaf spring with blade portions unfolded in the third embodiment, and FIG. 14(B) is an enlarged front view of a main part of FIG. 14(A). [Figure 15] FIG. 10 is a cross-sectional view showing a leaf spring according to a fourth embodiment. [Figure 16] 10A is a front view of a leaf spring in which blade portions are unfolded in a fifth embodiment, and FIG. 10B is a perspective view of the leaf spring in the fifth embodiment. [Figure 17] FIG. 17 is an enlarged front view of the main part of the leaf spring shown in FIG. 16(B). DETAILED DESCRIPTION OF THE INVENTION

[0020] A first embodiment of the present invention will be described below with reference to FIGS. 1 to 10. In the following description, the direction in which an axis L of a guide portion 10 (described later) extends will be referred to as the "axis L direction," one side of the axis L direction will be referred to as the "one side L1," and the other side will be referred to as the "other side L2." A direction perpendicular to (intersecting) the axis L direction will be referred to as the "radial direction X." In the radial direction X, the side of the axis L will be referred to as the "inner side," and the side opposite the inner side will be referred to as the "outer side." Some drawings, such as FIG. 3, also refer to the inner side and the outer side. A valve device according to the first embodiment is used, for example, as a slide-type four-way switching valve 100 (slide-type switching valve) that switches the flow direction of a fluid in a refrigeration cycle system. The slide-type four-way switching valve 100 includes a valve housing 1 formed in a cylindrical shape using a metal material such as stainless steel. The valve housing 1 includes a cylindrical guide portion 10 extending in the axis L direction. A D port 11 penetrating the side wall of the guide portion 10 in the radial direction X is formed by burring or the like.

[0021] A D joint pipe 11a serving as a high-pressure pipe is fixed to the D port 11 by brazing or the like. One end of the D joint pipe 11a is connected to the discharge port of a compressor 600 (see FIG. 10 ), which will be described later, and a high-pressure fluid such as a refrigerant flows through the D joint pipe. A plate-shaped valve seat member 20 extending in the axial direction L is provided on the inner surface 10a of the side wall of the guide portion 10 at a position facing the D port 11. The inner surface of the valve seat member 20 in the radial direction X forms a valve seat surface 21 with which a valve disc 40, which will be described later, slides. An E port 22, an S port 23, and a C port 24 are formed in this order on the valve seat surface 21, penetrating the guide portion 10 in the radial direction X to the outside thereof, from one side L1 to the other side L2. An E joint pipe 22a, an S joint pipe 23a, and a C joint pipe 24a, which communicate with the inside and outside of the guide portion 10, are connected to the E port 22, the S port 23, and the C port 24, respectively, and are fixed by brazing or the like. The E joint pipe 22a, the S joint pipe 23a, and the C joint pipe 24a are pipes through which a refrigerant flows, similar to the D joint pipe 11a, and function as high-pressure pipes or low-pressure pipes. One end of the E joint pipe 22a is connected to an indoor heat exchanger 300 (see FIG. 10), which will be described later. One end of the S joint pipe 23a is connected to a suction port of a compressor 600 (see FIG. 10). One end of the C joint pipe 24a is connected to an outdoor heat exchanger 500 (see FIG. 10), which will be described later.

[0022] A cover member 30 is attached to each opening at both ends of the guide portion 10 in the axial direction L. The cover member 30 is made of metal and is formed in a generally bowl-like shape that opens inward in the axial direction L. The cover member 30 is fitted into mounting steps 12 formed with an enlarged diameter on the inner surface of the guide portion 10 at both ends in the axial direction L, and is fixed by welding or the like. By fixing the cover member 30, the inside of the guide portion 10 is sealed, and a valve chamber 13 is formed in the valve housing 1. The valve chamber 13 is divided into three spaces by a piston 50 (moving member) described below: a first working chamber 14 on one side L1, a central high-pressure chamber 15, and a second working chamber 16 on the other side. A cylindrical first working capillary 31 (capillary) is inserted into the wall surface of the cover member 30 arranged on one side L1. One end of the first working capillary tube 31 is connected to the inside and outside of the first working chamber 14, and the other end is connected to a pilot valve 200 (see Figure 10) described below, forming a flow path for flowing high-pressure or low-pressure working fluid that drives the piston 50.

[0023] On the other hand, a cylindrical second working capillary 32 (capillary) is inserted into the wall surface of the cover member 30 arranged on the other side L2. One end of the second working capillary 32 communicates with the inside and outside of the second working chamber 16, and the other end is connected to a pilot valve 200 (see FIG. 10), forming a flow path for flowing the working fluid to the second working chamber 16. A valve element 40 is installed within the valve housing 1. The valve element 40 has a bowl-shaped portion 41 with a recessed portion 41a that opens toward the valve seat surface 21, and a flange portion 42 that protrudes outward from the opening edge of the recessed portion 41a, and is connected to and held by a piston 50 described below. The bottom surface of the flange portion 42 forms a seal surface 43 that slides against the valve seat surface 21. The seal surface 43 is normally pressed against the valve seat surface 21 by the pressure difference between the high-pressure chamber 15 and the E joint pipe 22a, the S joint pipe 23a, or the C joint pipe 24a. Due to this pressing, the valve body 40, while held by the piston 50, can move back and forth in the direction of the axis L with the seal surface 43 in sliding contact with the valve seat surface 21.

[0024] The size of the opening of the recessed portion 41a of the valve disc 40 is set to be large enough to cover two adjacent openings among the E port 22, the S port 23, and the C port 24. This size setting allows the valve disc 40 to move back and forth along the axis L, switching the communication state between the E port 22, the S port 23, the C port 24, and the D port 11. Specifically, when the recessed portion 41a is in the other side position L2 shown in FIG. 1 , it connects the S port 23 and the C port 24 internally and connects the D port 11 and the E port 22 externally. In this state, high-pressure refrigerant that flows into the valve chamber 13 through the D joint pipe 11a and the D port 11 flows toward the valve seat member 20 through a pressure equalizing hole 62 (described later) and then flows to the E joint pipe 22a via the E port 22, which is not covered by the recessed portion 41a. On the other hand, the low-pressure refrigerant that has flowed into the recessed portion 41a through the C joint pipe 24a and the C port 24 flows through the S port 23 to the S joint pipe 23a.

[0025] In contrast, when the valve disc 40 moves from the other side L2 position to the one side L1 position (not shown), the recessed portion 41a internally connects the E port 22 and the S port 23, and externally connects the D port 11 and the C port 24. In this state, high-pressure refrigerant that flows into the valve chamber 13 through the D joint pipe 11a and the D port 11 flows through the pressure equalizing hole 62 toward the valve seat member 20 and into the C joint pipe 24a via the C port 24, which is not covered by the recessed portion 41a. On the other hand, low-pressure refrigerant that flows into the recessed portion 41a through the E joint pipe 22a and the E port 22 flows into the S joint pipe 23a via the S port 23. In this way, the flow of fluid is controlled by the back-and-forth movement of the valve disc 40 in the direction of the axis L.

[0026] A piston 50 (moving member) that moves along the axis L is installed inside the valve housing 1. The piston 50 is equipped with a connecting member 60 that holds the valve element 40. The connecting member 60 is formed by bending a metal material such as stainless steel, and is formed in a plate shape that extends in the direction of the axis L. An oval valve element holding hole 61 that penetrates the connecting member 60 in the plate thickness direction (radial direction X) is formed in the center of the connecting member 60. The bowl-shaped portion 41 of the valve element 40 is inserted into the valve element holding hole 61 and held in that state. In other words, the valve element 40 is connected to the piston 50. Circular pressure equalizing holes 62 that penetrate the valve element holding hole 61 in the plate thickness direction (radial direction X) are formed on one side L1 and the other side L2 of the valve element holding hole 61. The pressure equalizing holes 62 communicate between the D port 11 side of the high-pressure chamber 15 and the valve seat member 20 side of the high-pressure chamber 15. Both end portions of the connecting member 60 in the direction of the axis L are bent outward in the radial direction X, and a seal portion 70 is attached to each of the surfaces of the bent portions on the outer side in the direction of the axis L.

[0027] The seal portion 70 is a partition wall that divides the valve chamber 13 into a first working chamber 14, a high-pressure chamber 15, and a second working chamber 16 (dividing the valve chamber 13 into multiple spaces), and as shown in FIG. 2, includes a first reinforcing member 71, a second reinforcing member 72, an L-packing 80, and a leaf spring 90. While FIG. 2 shows the structure of the seal portion 70 disposed on the other side L2 of the valve chamber 13, the seal portion 70 disposed on one side L1 has a similar structure, and therefore detailed description and illustration of the seal portion 70 on one side L1 will be omitted. The first reinforcing member 71 is a plate member disposed on one side L1 of the leaf spring 90, and is formed in a disk shape with approximately the same outer diameter as the base portion 91 of the leaf spring 90. The first reinforcing member 71 has a rivet hole 71a and a screw hole (not shown) that penetrate in the direction of the axis L. The second reinforcing member 72 is a plate member that is arranged on the other side L2 of the L-packing 80, and is formed in a disk shape with an outer diameter larger than that of the base 81 of the L-packing 80.

[0028] The second reinforcing member 72 not only reinforces the seal portion 70, but also functions as a stopper that restricts movement of the piston 50 by abutting against the opening edge of the cover member 30 described above within the guide portion 10. The second reinforcing member 72 is formed with rivet holes 72a and screw holes (not shown) that penetrate in the direction of the axis L. The L-packing 80 is made of, for example, a resin material such as Teflon (registered trademark), or an elastic material such as elastomer or rubber, and includes a base portion 81 extending in the radial direction X and a rim portion 82 rising inward in the direction of the axis L from the edge of the base portion 81. The base portion 81 is formed in a disk shape and extends perpendicular to the axis L. As shown in FIG. 1 , a screw hole 83 and a rivet hole 84 that penetrate in the direction of the axis L (thickness direction) are formed in the plate surface of the base portion 81.

[0029] The rim portion 82 is formed with a diameter that increases toward the inside in the direction of the axis L so as to be positioned outward in the radial direction X, and is elastically deformable in the radial direction X (plate thickness direction). As shown in FIG. 3(A), before elastic deformation, the outer surface 82a at the tip end of the rim portion 82 is positioned outward from the inner surface 10a of the side wall of the guide portion 10, which is shown by the imaginary line. In other words, the outer diameter at the tip end of the rim portion 82 before elastic deformation is larger than the inner diameter of the guide portion 10. Then, when the seal portion 70 is installed in the guide portion 10, the rim portion 82 elastically deforms inward and reduces in diameter, and fits into the inner surface 10a of the side wall of the guide portion 10, as shown in FIG. 3(B). In this state, the outer surface 82a of the rim portion 82 is able to slide against the inner surface 10a of the guide portion 10.

[0030] The leaf spring 90 is a member that acts on the L-packing 80 to press the L-packing 80 against the guide portion 10, and is made of a metal material. The leaf spring 90 has a disk-shaped base plate portion 91 that extends in the radial direction X. The base plate portion 91 is arranged in a stacked state on the inner surface side (one side L1 in FIG. 3(B)) of the base portion 81 of the L-packing 80. As shown in FIG. 4(A), screw holes 91a and rivet holes 91b that penetrate in the direction of the axis L (plate thickness direction) are formed on the plate surface of the base plate portion 91. A plurality of blade portions 92 are formed on the outer periphery of the base plate portion 91. As shown in FIG. 4(B), the blade portions 92 are provided so as to protrude radially from the axis L as the center, and as shown in FIG. 4(A), the blade portions 92 are arranged to protrude radially from the axis L as the center, and rise from the base plate portion 91 by bending the tip side starting from the boundary with the base plate portion 91.

[0031] In this embodiment, a total of 24 blade portions 92 are formed at equal intervals in the circumferential direction around axis L, but the number of blade portions 92, the intervals between adjacent blade portions 92, and the like may be changed as appropriate. As shown in FIG. 5(A) , each blade portion 92 includes a first bent portion 93 (bent portion) that forms the boundary with base portion 91, and a first blade portion 94 (plate portion) that rises from first bent portion 93. Furthermore, each blade portion 92 includes a second bent portion 95 (edge ​​portion) that is provided on the tip side of first blade portion 94, and a second blade portion 96 (second plate portion) that extends inward in the radial direction X (toward the inner side of leaf spring 90) from second bent portion 95. The inner and outer surfaces of first bent portion 93 are formed to have an arc-shaped R-shape, and are formed near the outer peripheral edge of base portion 91, which is formed in the shape of a disk as described above. However, without being limited to this, for example, a protrusion that protrudes radially outward may be formed in advance at the position where blade portion 92 is to be formed on the outer peripheral edge portion of base portion 91, and first bent portion 93 may be formed on the protruding end edge of the protrusion. In other words, first bent portion 93 may be formed on base portion 91 that is formed not in a disk shape but in a shape in which a protrusion protrudes from a disk.

[0032] The first blade portion 94 is formed in a flat plate shape, and its width dimension decreases from the first bent portion 93 side toward the second bent portion 95 side. As shown in FIG. 5(B), the first blade portion 94 extends at an angle so as to be positioned outward in the radial direction X toward one side L1. As shown in FIG. 5(A), both widthwise ends of the first blade portion 94 extend linearly from the first bent portion 93 toward the second bent portion 95, forming linear portions connecting the first bent portion 93 and the second bent portion 95. The second bent portion 95 is formed by bending the one side L1 (tip side) of the blade portion 92 inward in the radial direction X, and forms an edge portion of the first blade portion 94 and a boundary portion between the first blade portion 94 and the second blade portion 96. As shown in Fig. 5(B), the second blade portion 96 extends from the second bent portion 95 to one side L1, toward a position further inward in the radial direction X than the extension direction of the first blade portion 94. As shown in Fig. 6, abutment portions 97 that abut against the rim portion 82 are provided on both ends of the blade portion 92 in the width direction. The abutment portions 97 straddle the second bent portion 95 and have a predetermined length spanning from the first blade portion 94 to the second blade portion 96.

[0033] As shown in FIG. 7, the abutting portions 97 extend between a first imaginary line b1 and a second imaginary line b2, which are substantially perpendicular to an imaginary radial line a1 connecting the axis L and the center of the tip of the blade portion 92. The abutting portions 97 are inclined in directions approaching each other as they approach the protruding side of the blade portion 92. As a result, the abutting portions 97 extend intersecting with the imaginary line a2 that extends radially from the axis L. The blade portion 92 configured in this manner is elastically deformable in the radial direction X, starting from the first bent portion 93. As shown in FIG. 8(A), in the blade portion 92 before elastic deformation, the outer surface portion 97a of the abutting portion 97 is located outward in the radial direction X from the abutted portion 82b, which is the abutting target of the rim portion 82 before deformation and is shown by the imaginary line. That is, before elastic deformation, the outer diameter of a portion of leaf spring 90 where contact portion 97 is located is larger than the inner diameter of a portion of rim portion 82 where contacted portion 82b is located. Then, when seal portion 70 is assembled, as shown in FIG. 8(B), contact portion 97 of blade portion 92 elastically deforms inward in radial direction X, reducing its diameter, and contacts contacted portion 82b of rim portion 82 while sinking in the plate thickness direction.

[0034] As described above, since at least a portion of both widthwise ends of blade portion 92 is formed as abutment portion 97, if leaf spring 90 is provided with n blade portions 92, leaf spring 90 will be provided with 2n abutment portions 97. As shown in FIG. 9(A), in this embodiment, a total of 24 blade portions 92 are formed, and therefore a total of 48 abutment portions 97 are provided. The multiple blade portions 92 formed in this manner are connected by arc portions 91c formed on the edge of base portion 91, as shown in FIG. 9(B). Arc portions 91c are formed by cutting out the edge of base portion 91 in a convex arc shape on the side opposite the protruding direction of blade portions 92, and connect first bent portions 93 of adjacent blade portions 92.

[0035] Increasing the radius of the arc portion 91c increases the spacing between adjacent blade portions 92, making it difficult to increase the number of blade portions 92 in a base portion 91 of the same circumferential length. Therefore, from the perspective of ensuring the number of blade portions 92, it is preferable to set the radius of the arc portion 91c as small as possible. On the other hand, if the radius of the arc portion 91c is too small, the management costs of the mold for forming the leaf spring 90 increase. Therefore, from the perspective of reducing the manufacturing cost of the leaf spring 90, it is preferable to maintain the radius of the arc portion 91c at a predetermined value. Specifically, as shown in FIG. 9(B), where R is the radius of the arc portion 91c and t is the thickness of the blade portion 92, it is desirable to satisfy the relationship t≦R≦5t. With this configuration, the radius R of the arc portion 91c can be limited to a maximum of approximately five times the thickness t of the blade portion 92, making it easier to position adjacent blade portions 92 relatively close to each other. On the other hand, by making the radius R of the arc portion 91c equal to or greater than the thickness dimension t of the blade portion 92, it is possible to prevent the radius R from becoming too small, and to keep the management costs of the mold at a reasonable level.

[0036] The L-shaped packing 80, leaf spring 90, first reinforcing member 71, and second reinforcing member 72 formed in this manner are integrated with rivets 73 and fixed to both end portions of the connecting member 60 in the axial direction L with bolts 74. Specifically, as shown in FIG. 2(A), the first reinforcing member 71, leaf spring 90, L-shaped packing 80, and second reinforcing member 72 are stacked in this order from one side L1 to the other side L2. In this state, the first reinforcing member 71, leaf spring 90, L-shaped packing 80, and second reinforcing member 72 are fixed together with rivets 73 inserted through rivet holes 71a, 91b, 84, and 72a. The seal portion 70 is then fixed to the connecting member 60 with bolts 74. Specifically, the seal portion 70 is fixed to both ends of the connecting member 60 in the direction of the axis L by bolts 74 that are inserted through a screw hole (not shown) in the first reinforcing member 71, a screw hole 91a in the leaf spring 90, a screw hole 83 in the L-type packing 80, and a screw hole (not shown) in the second reinforcing member 72. The L-type packing 80 of the seal portion 70, which is integrated with the connecting member 60, is installed inside the guide portion 10. The L-type packing 80 installed inside the guide portion 10 fits into the inner surface 10a of the side wall of the guide portion 10.

[0037] When the L-type packing 80 is fitted, the rim portion 82, which has deformed inward in the radial direction X, presses the blade portions 92 of the leaf spring 90, causing them to elastically deform inward in the radial direction X. Then, a force that attempts to return the blade portions 92 to their pre-elastic deformation presses the rim portion 82 from the inner surface to the outer surface via the abutment portions 97. This pressing force presses the rim portion 82 against the inner surface 10a of the guide portion 10. Furthermore, a force that attempts to return the rim portion 82 to its pre-elastic shape presses the rim portion 82 against the inner surface 10a of the guide portion 10. These pressing forces create a sealed state between the seal portion 70 and the guide portion 10, preventing fluid leakage between the first working chamber 14, the high-pressure chamber 15, and the second working chamber 16. At this time, as shown in FIG. 9A , the blade portions 92 are arranged at equal intervals in the circumferential direction around the axis L, thereby preventing unevenness in the pressing force pressing the rim portion 82.

[0038] For example, in a leaf spring such as that described in Patent Document 1, in which the width of the blades increases from the base to the tip, the following problem is likely to occur. Specifically, when a load is applied to the tip of the blade 41b due to deformation of the rim 45b shown in FIGS. 2 and 3 of Patent Document 1, the width of the base of the blade 41b, where greater stress occurs, is narrower. This results in insufficient strength at the base, and the overall design load of the leaf spring 41 is likely to be reduced. Furthermore, in this configuration, the distance between the end point P of one blade 41b and the end point P of another blade 41b adjacent to the first blade 41b is likely to be smaller than the distance between two end points P (contact points) of the first blade 41b. This makes it difficult to evenly arrange the multiple end points P in the circumferential direction around the axis L, which tends to result in uneven pressing force on the rim 45b. To resolve this uneven pressing force, the leaf spring 41 needs to be enlarged, which increases the overall size of the motor-operated valve.

[0039] Furthermore, when second bent portion 41b2 (second bent portion) is formed and brought into contact with rim portion 45b, end point P is likely to come into point contact. This makes it difficult to increase the contact area between blade portion 41b and rim portion 45b, and therefore difficult to improve the sealing performance of seal portion 4. Furthermore, rim portion 45b, which is the contact point of end point P, is formed in a cylindrical shape that follows the inner circumferential shape of guide portion 21, and therefore the inner surface of rim portion 45b that directly contacts end point P is arc-shaped. In this case, both widthwise ends of blade portion 41b include end point P and extend along radial lines centered on axis X, so the tip corners of blade portion 41b are likely to interfere with rim portion 45b.

[0040] In contrast, in the first embodiment, as shown in FIG. 9(B), the width W2 of the second bent portion 95 of each blade 92 is set smaller than the width W1 (root width) of the first bent portion 93 of each blade 92. This setting makes it easier to ensure the required strength at the first bent portion 93, where greater stress is generated. This allows the multiple blades 92 to favorably bear the load, increasing the overall design load of the leaf spring 90. Furthermore, making the width W2 smaller than the width W1 facilitates the following: It makes it easier to set the spacing S1 (abutment width) between the contact portions 97 of one blade 92 and the spacing S2 (gap width) between the contact portions 97 of one blade 92 and the contact portion 97 of another blade 92 adjacent to the one blade 92 to be approximately the same, without increasing the size of the leaf spring 90. This prevents the leaf spring 90 from becoming too large, while preventing the pressing force against the rim portion 82 from becoming locally insufficient, and the sealing performance of the seal portion 70 is stably maintained.

[0041] The relationship between the distance S1 (contact portion width) and the distance S2 (gap width) is preferably 0.8≦S1 / S2≦1.2, and more preferably S1=S2. As described above, in the first embodiment, the contact portions 97 are inclined toward each other toward the protruding side of the blade portion 92. This increases the contact area between the blade portion 92 and the rim portion 82, as described below, and improves the sealing performance of the seal portion 70. That is, when comparing seal members 70 each having a base portion 91 with the same circumferential length, the same number of blade portions 92, and the same circumferential length of the rim portion 82, the width dimension W2 of the second bent portion 95 in this embodiment is smaller than that of a configuration in which the contact portions 97 are inclined toward each other toward the protruding side of the blade portion 92 (for example, the blade portion 41b shown in FIG. 3 of Patent Document 1, hereinafter referred to as the conventional configuration). This makes it easier to suppress deformation between the widthwise ends of the second bent portion 95 when force is applied between the abutment portions 97, compared to the conventional configuration, and allows the abutment portions 97 to reliably abut against the rim portion 82. At this time, the abutment portions 97 can be caused to sink deeply into the rim portion 82 and make contact as a linear surface. Therefore, as described above, the contact area between the blade portion 96 and the rim portion 82 can be increased, improving the sealing performance of the seal portion 70. Furthermore, with this configuration, the widthwise ends of the blade portion 92, including the abutment portions 97, do not extend along radial lines centered on the axis L, making it less likely that the tip corners of the second blade portions 96 will interfere with the inner surface of the rim portion 82. This more stably maintains the state in which the blade portion 92 presses against the rim portion 82.

[0042] Next, the operation of the slide-type four-way selector valve 100 will be described. As shown in FIG. 10 , the slide-type four-way selector valve 100 constitutes a refrigeration cycle system together with, for example, a compressor 600, an indoor heat exchanger 300, a throttling device 400, and an outdoor heat exchanger 500. The working fluid controlled by the pilot valve 200 drives the piston 50, switching the flow path of a fluid such as a refrigerant and switching between a heating mode and a cooling mode. For example, in the heating mode, as shown in FIG. 10 , high-pressure working fluid controlled by the pilot valve 200 flows into the first working chamber 14 via the first working capillary tube 31. Meanwhile, low-pressure working fluid flows into the second working chamber 16 via the second working capillary tube 32. This causes the piston 50 to move to the other side L2 due to the pressure difference between the first working chamber 14 and the second working chamber 16. Then, the second reinforcing member 72 on the other side L2 comes into contact with the opening edge of the cover member 30 on the other side L2, stopping the movement of the piston 50. As a result, the valve element 40 is located at the other side L2 position, as shown in Fig. 10. In this state, high-pressure refrigerant flowing from the discharge port of the compressor 600 flows in the following order: D joint pipe 11a, D port 11, the D port 11 side of the valve chamber 13, the pressure equalizing hole 62, the valve seat member 20 side of the valve chamber 13, E port 22, E joint pipe 22a, the indoor heat exchanger 300, and the expansion device 400. Similarly, low-pressure refrigerant flowing from the outdoor heat exchanger 500 flows in the following order: C joint pipe 24a, C port 24, the recessed portion 41a, the S port 23, the S joint pipe 23a, and the suction port of the compressor 600.

[0043] On the other hand, in the cooling mode, high-pressure working fluid controlled by the pilot valve 200 flows into the second working chamber 16 via the second working capillary tube 32. Low-pressure working fluid also flows into the first working chamber 14 via the first working capillary tube 31. This causes the piston 50 to move toward the first side L1 due to the pressure difference between the first working chamber 14 and the second working chamber 16. The second reinforcing member 72 on the first side L1 then abuts against the opening edge of the cover member 30 on the first side L1, stopping the movement of the piston 50. This positions the valve element 40 at the first side L1 position (not shown). In this state, high-pressure refrigerant flowing from the discharge port of the compressor 600 flows sequentially through the D joint pipe 11a, the D port 11, the D port 11 side of the valve chest 13, the pressure equalizing hole 62, the valve seat member 20 side of the valve chest 13, the C port 24, the C joint pipe 24a, the outdoor heat exchanger 500, and the expansion device 400. Furthermore, the low-pressure refrigerant flowing from the indoor heat exchanger 300 flows in this order through the E joint pipe 22a, the E port 22, the recessed portion 41a, the S port 23, the S joint pipe 23a, and the suction port of the compressor 600. Even when the piston 50 is driven in this manner, the seal portion 70 maintains a tight seal between the piston 50 and the valve housing 1, and fluid leakage between the first working chamber 14, the high-pressure chamber 15, and the second working chamber 16 is restricted.

[0044] Next, a modified example of the first embodiment will be described. FIG. 11(A) is a perspective view of a leaf spring 90A according to a modified example of the first embodiment, and FIG. 11(B) is a front view showing the dimensional relationship of the leaf spring 90A including the blade portion 92A shown in FIG. 11(A). FIG. 11(C) is a front view of the leaf spring 90A with the blade portion 92A shown in FIG. 11(A) unfolded. As shown in FIG. 11(A), in the modified example, the shape of the blade portion 92A differs from that of the first embodiment. Specifically, as shown in FIG. 11(B), the width dimension of the first blade portion 94A (plate portion) is uniform from the first bent portion 93A (bent portion) side toward the second bent portion 95A (edge ​​portion) side. That is, the second bent portion 95A of the blade portion 92A and the first bent portion 93A of the blade portion 92A have the same width dimension W3. 11(C), the width of blade 92 at the portion where abutment portion 97A is located remains constant toward second blade 96 (second plate portion). This modification makes it easier to keep constant the stress generated on the first bent portion 93A side and the second bent portion 95A side of blade 92A, allowing the set load of leaf spring 90A to be increased.

[0045] As described above, according to the first embodiment and the modified example described above, the width dimension of the first blade portion 94 (first blade portion 94A) decreases or remains constant from the first bent portion 93 (first bent portion 93A) side toward the second bent portion 95 (second bent portion 95A) side, which makes it easier to reduce the width dimension of the second bent portion 95 that abuts against the rim portion 82. This makes it easier to evenly arrange the second bent portions 95 in the circumferential direction about the axis L. This prevents localized insufficient pressing against the rim portion 82, and ensures stable sealing performance by the seal portion 70. Furthermore, with this configuration, the width dimension of the first blade portion 94 is either larger on the first bent portion 93 side than on the second bent portion 95 side, or remains constant. For this reason, it is easy to ensure the required strength on the first bent portion 93 side (the base side of the blade portion) where greater stress occurs when a load is applied from the rim portion 82 to the blade portion 92 (blade portion 92A) via the second bent portion 95, and the plurality of blade portions 92 can favorably bear the load. This allows the design load of the entire leaf spring 90 (leaf spring 90A) to be increased, and the tension of the rim portion 82 can be stably maintained even in an environment where the seal portion 70 expands or contracts due to temperature changes. Therefore, it is possible to provide a sliding four-way selector valve 100 (valve device) that is less susceptible to temperature changes and can stably maintain sealing performance.

[0046] Furthermore, according to the first embodiment and the modified examples, both widthwise ends of first wing portion 94 of leaf spring 90 form straight portions that connect first bent portion 93 and second bent portion 95. With this configuration, no special processing is required for both widthwise ends of first wing portion 94, and the shape of first wing portion 94 can be simplified, thereby reducing mold production costs and enabling seal portion 70 to be produced at low cost.

[0047] Furthermore, according to the first embodiment and its modified examples, when the radius of the arc-shaped portion 91c of the leaf spring 90 is R and the thickness of the blade portion 92 is t, the relationship t≦R≦5t is satisfied. With this configuration, the radius R of the arc-shaped portion 91c can be limited to a maximum of approximately five times the thickness t of the blade portion 92, making it easier to position adjacent blade portions 92 relatively close to each other. This increases the number of blade portions 92 that can be formed on the base portion 91 per circumferential length, distributes the load applied to the blade portions 92, and more stably maintains the state in which the blade portions 92 press against the rim portion 82. Note that if the radius R of the arc-shaped portion 91c is too small, the management costs of the mold for forming the leaf spring 90 increase. However, according to this configuration, the radius R of the arc-shaped portion 91c is set to be equal to or greater than the thickness t of the blade portion 92, preventing the radius R from becoming too small and keeping the management costs of the mold at a reasonable level.

[0048] Furthermore, according to the first embodiment and the modified example, the abutment portions 97 (abutment portions 97A) have a predetermined length spanning the second bent portions 95, and are inclined toward each other or parallel toward the protruding side of the blade portions 92. Therefore, as described above, when comparing seal member 70 materials having base portions 91 with the same circumferential length, the same number of blade portions 92, and rim portions 82 with the same circumferential length, the abutment portions 97A are more likely to suppress deformation between the widthwise ends of the second bent portions 95 when force is applied between the abutment portions 97 than the conventional configuration. Therefore, the abutment portions 97 can be made to sink deeply into the rim portions 82 and make contact as a linear surface. This increases the contact area between the blade portions 92 and the rim portions 82, improving the sealing performance of the seal member 70.

[0049] Furthermore, according to the first embodiment and its modified examples, by arranging twice the number of abutment portions 97 as the number of blades 92 evenly in the circumferential direction, it is possible to make the uniform gaps between the abutment portions 97 smaller than in a configuration in which the blades 92 press against the rim portion 82 at a single point. This allows the shape of the multiple abutment portions 97 connected to each other to approximate a regular polygon. This makes it less likely that the pressure on the rim portion 82 will be locally insufficient, further preventing the rim portion 82 from lifting up from the inner surface of the guide portion 10.

[0050] Furthermore, according to the first embodiment and the modified examples, it is possible to provide a refrigeration cycle system that is less susceptible to the effects of temperature changes and is capable of stably maintaining sealing performance.

[0051] In the first embodiment and the modified example, the blade portion 92 (blade portion 92A) of the leaf spring 90 (leaf spring 90A) is configured with the first bent portion 93 (first bent portion 93A), the first blade portion 94 (first blade portion 94), the second bent portion 95 (second bent portion 95A), and the second blade portion 96. However, the configuration of the blade portion 92 is not limited to this. FIGS. 12A and 12B are cross-sectional views showing variations of the leaf spring 90. As shown in FIG. 12A, the leaf spring 90 includes a third bent portion α1 between the first bent portion 93 and the second bent portion 95, and a fourth bent portion α2 in the second blade portion 96. The third bent portion α1 and the fourth bent portion α2 serve as starting points for bending the blade portion 92 toward the inside of the leaf spring 90. Note that bent portions such as third bent portion α1 and fourth bent portion α2 may be further added to form a fifth bent portion, a sixth bent portion, etc. In this way, blade portion 92 may be provided with a plurality of bent portions other than first bent portion 93 and second bent portion 95 between first bent portion 93 and second bent portion 95, or on the second blade portion 96 side of second bent portion 95. Also, as shown in FIG. 11(B), first blade portion 94 does not necessarily have to be formed in a flat plate shape, and may be formed to be curved toward the outside of leaf spring 90, with the plate surface thereof forming a curved surface β.

[0052] Next, a second embodiment of the present invention will be described. FIG. 13(A) is a front view of a leaf spring 90B in the second embodiment with the blade portion 92B unfolded, and FIG. 13(B) is an enlarged front view of the main portion of FIG. 13(A). As shown in FIG. 13(A), in the second embodiment, the shape of the blade portion 92B differs from the shapes of the blade portion 92 and the blade portion 92A described above. Specifically, as shown in FIG. 13(B), both widthwise ends of the first blade portion 94B (plate portion) do not have straight portions, but are composed of a tapered portion 98a on the first bent portion 93B (bent portion) side and a straight portion 98b on the second bent portion 95B (edge ​​portion) side. The tapered portions 98a are inclined in a direction approaching each other as they approach the second bent portion 95B side. The straight portions 98b are continuous with the tapered portion 98a on the second bent portion 95B side and are parallel to each other as they approach the second bent portion 95B side.

[0053] With this configuration, the width of the blade portion 92B is smaller on the straight portion 98b side than on the tapered portion 98a side, making it easier to reduce the width of the second bent portion 95B that abuts against the rim portion 82. This makes it easier to evenly distribute the second bent portions 95B in the circumferential direction around the axis L. Furthermore, with this configuration, the width of the blade portion 92B is larger on the tapered portion 98a side than on the straight portion 98b side. This makes it easier to ensure the required strength on the tapered portion 98a side (the base side of the blade) where greater stress occurs when a load is applied to the blade portion 92B from the rim portion 82 via the second bent portion 95B. This allows the multiple blade portions 92B to favorably bear the load. This increases the design load of the entire leaf spring 90B, enabling the tension of the rim portion 82 to be stably maintained even in an environment where the seal portion 70 expands or contracts due to temperature changes.

[0054] Next, a third embodiment of the present invention will be described. Fig. 14(A) is a front view of a leaf spring 90C in the third embodiment with a blade portion 92C unfolded, and Fig. 14(B) is an enlarged front view of a main portion of Fig. 14(A). As shown in Fig. 14(A), in the third embodiment, the shape of the blade portion 92C differs from the shapes of the blade portions 92, 92A, and 92B described above. Specifically, as shown in Fig. 14(B), both widthwise ends of the first blade portion 94C (plate portion) are not linear but are formed by curved portions 99. The curved portions are formed in smooth curves that converge toward the second bent portion 95C (edge ​​portion). Note that the curved portion 99 shown in Fig. 14(B) is elliptical, but may be formed in various curved shapes, such as a single R shape or a parabolic shape.

[0055] With this configuration, the width of the blade 92C is smaller on the second bent portion 95C side of the curved portion 99 than on the first bent portion 93C side. This makes it easier to reduce the width of the second bent portion 95C that abuts against the rim portion 82. This makes it easier to evenly distribute the second bent portions 95C in the circumferential direction around the axis L. This configuration also makes the width of the blade 92C larger on the first bent portion 93C side of the curved portion 99 than on the second bent portion 95C side. This makes it easier to ensure the required strength on the first bent portion 93C side (the base side of the blade) where greater stress occurs when a load is applied from the rim portion 82 to the blade 92C via the second bent portion 95C. This allows the multiple blades 92C to favorably bear the load. This increases the design load of the entire leaf spring 90C, and stably maintains the tension of the rim portion 82 even in an environment where the seal portion 70 expands or contracts due to temperature changes.

[0056] Next, a fourth embodiment of the present invention will be described. Fig. 15 is a cross-sectional view showing a leaf spring 90D according to the fourth embodiment. As shown in Fig. 15, in the fourth embodiment, the shape of a blade 92D is different from that of blade 92, blade 92A, blade 92B, and blade 92C. Specifically, blade 92D has an edge portion 95D corresponding to second bent portion 95 at the tip end of first blade 94D corresponding to second bent portion 95. Furthermore, second blade 96 is omitted from blade 92D. In this blade 92D, the width dimension of first blade 94D decreases or remains constant from the first bent portion 93D (bent portion) side toward edge portion 95D.

[0057] As shown in FIG. 15 , abutment portions 97D are provided at both widthwise ends of blade portion 92D. The abutment portions 97D correspond to the aforementioned abutment portions 97. While not shown in detail, the abutment portions 97D have a predetermined length from edge portion 95D toward first bent portion 93D and are inclined toward each other or parallel toward the protruding side of blade portion 92D. According to the fourth embodiment, as described above, when comparing seal member 70 members each having a base plate portion 91D with the same circumferential length, the same number of blade portions 92D, and a rim portion 82 with the same circumferential length, deformation between both widthwise ends of edge portion 95D when force is applied between the abutment portions 97D is more easily suppressed than in the conventional configuration. Therefore, the abutment portions 97D can be made to sink deeply into the rim portion 82 and make contact as a linear surface. This increases the contact area between blade portion 92D and rim portion 82, improving the sealing performance of seal portion 70.

[0058] Next, a fifth embodiment of the present invention will be described. FIG. 16(A) is a front view of a leaf spring 90E in the fifth embodiment with the blades 92E unfolded, and FIG. 16(B) is a perspective view of the leaf spring 90E of the fifth embodiment. FIG. 17 is an enlarged front view of a main portion of the leaf spring 90E shown in FIG. 16(B). As shown in FIG. 16(A), in the fifth embodiment, the shape of the blades 92E is different from that of the blades 92, 92A, 92B, 92C, and 92D. Specifically, as shown in FIGS. 16(A) and 16(B), the width of the blades 92E increases from the first bent portion 93E (bent portion) side toward the second bent portion 95E (edge ​​portion). Due to this shape, the number of blades 92E formed on the leaf spring 90E is 18. As shown in FIG. 17, an edge 95f connecting both widthwise ends 95d of the second bent portion 95E on the outer surface side of the second bent portion 95E is formed in an arc shape.

[0059] The curvature of edge 95f is set to be approximately the same as the curvature of the inner surface of rim portion 82 and the curvature of inner surface 10a of the side wall of guide portion 10 against which rim portion 82 is pressed. Both widthwise ends 95d and edge 95f of second bent portion 95E constitute contact portion 97E of the fifth embodiment. Here, as described above, particularly in a configuration in which both widthwise ends of second bent portion 95 are pressed against rim portion 82, the pressing force against rim portion 82 between these ends may be insufficient.

[0060] This is likely to be particularly noticeable in a valve device such as that described in Patent Document 1, for example. Specifically, in the blades 41b of the leaf spring shown in Figures 2 and 3 of Patent Document 1, the tip side is formed wider than the base side, which tends to increase the distance between the end points P of one blade 41b. As a result, the pressing force against the rim portion 45b between the end points P of one blade 41b is particularly insufficient. In this case, if the rim portion 45b contracts (thermally deforms) due to a temperature drop, for example, the rim portion 45b may rise toward the blades 41b between the end points P, potentially resulting in fluid leakage.

[0061] In this regard, in the leaf spring 90E of the fifth embodiment, in addition to the widthwise end portions 95d of the blade portions 92E, the edge portions 95f, which have a curvature substantially identical to the curvature of the inner surface of the rim portion 82 and the curvature of the inner surface 10a of the side wall of the guide portion 10, serve as the abutment portions 97E. This allows the contact area between the blade portion 92E and the rim portion 82 to be efficiently and uniformly increased between the end portions 95d of each blade portion 92E, effectively preventing the rim portion 82 from lifting up. This provides a sliding four-way selector valve 100 that is less susceptible to temperature changes and can stably maintain sealing performance. The edge portions 95f of the fifth embodiment may also be applied to the first embodiment, modified examples, second embodiment, third embodiment, and fourth embodiment. In other words, even in a configuration in which the width dimension of the blade portion 92 becomes smaller or remains the same from the first bending portion 93 side to the second bending portion 95 side, an abutment portion 97 may be formed having a curvature that is approximately the same as the curvature of the inner surface of the rim portion 82 and the curvature of the inner surface 10a of the side wall of the guide portion 10.

[0062] The above-described embodiment and modified examples merely illustrate typical aspects of the present invention, and the present invention is not limited thereto. For example, the valve device has been described as a slide-type four-way switching valve 100 driven by a pilot valve (not shown) and used in a refrigeration cycle system. However, this is merely an example, and the valve device may also be an electric valve equipped with a stepping motor and a screw feed mechanism. The valve device may also be a solenoid valve equipped with an electromagnetic coil and a plunger. While the valve device of this embodiment functions as a four-way valve that switches the flow of each of four flow paths, the number of flow paths is not limited to this and may be less than four or more than four. That is, the present invention can also be applied to two-way valves and three-way valves. The valve device may also be a mechanical expansion valve as a throttle device, a mechanical pressure regulating valve that drives a pressure-sensitive member connected to a valve element in response to pressure fluctuations, or a manual on-off valve equipped with an operating unit that moves a valve element back and forth. The valve device may also be used in applications other than refrigeration cycle systems, and the valve device of the present invention may be used in configurations that control various fluids. [Explanation of symbols]

[0063] L axis 10 Guide section 14 First working chamber (multiple spaces) 15 Hyperbaric Chambers (Multiple Rooms) 16 Second working chamber (multiple spaces) 40 Valve body 50 Piston (moving part) 70 Seal part 80 L packing 81 Base 82 Rim 90 Leaf spring 91 Circuit Board 92 Wing 93 First bending section (bending section) 94 First blade part (plate part) 95 Second bending part (edge ​​part) 100 Slide-type four-way switching valve (valve device, slide-type switching valve)

Claims

1. A valve device comprising: a cylindrical guide portion; a moving member that moves along an axis of the guide portion; and a valve body that is connected to the moving member and controls a flow of a fluid, The movable member is provided with a seal portion that divides the space within the guide portion into a plurality of spaces, The seal portion includes an L-shaped packing that fits onto the inner surface of the guide portion, and a leaf spring that acts on the L-shaped packing, The L-shaped packing includes a plate-shaped base portion extending intersecting the axis, and a rim portion rising from an edge of the base portion and in sliding contact with an inner surface of the guide portion, the leaf spring includes a plate-shaped base plate portion disposed on the inner surface side of the base portion, and a plurality of blade portions provided to protrude radially from the base plate portion around the axis line, and which press the rim portion from the inner surface side to the outer surface side, thereby pressing the rim portion against the guide portion; the blade portion includes a bent portion that forms a boundary with the base portion, a plate portion that rises from the bent portion, and an edge portion that is provided on a tip side of the plate portion and abuts against the rim portion, The valve device is characterized in that the width dimension of the plate portion decreases or remains constant from the bent portion side toward the edge portion side.

2. 2. The valve device according to claim 1, wherein both widthwise ends of the plate portion have straight portions connecting the bent portions and the edge portions.

3. 2. The valve device according to claim 1, wherein both widthwise ends of the plate portion include a tapered portion inclined toward each other as they approach the edge portion, and a straight portion that is continuous with the edge portion side of the tapered portion, extends toward the edge portion, and is parallel to each other.

4. 2. The valve device according to claim 1, wherein both widthwise ends of the plate portion are provided with curved portions that approach each other toward the edge portions.

5. an edge of the base plate portion is provided with an arc portion connecting the bent portions of the adjacent blade portions; The arc portion is formed in a convex arc shape on the opposite side to the protruding direction of the blade portion, When the radius of the arc portion is R and the thickness of the blade portion is t, 2. The valve device according to claim 1, wherein t≦R≦5t.

6. a contact portion that contacts the rim portion is provided at each of both widthwise end portions of the blade portion, The valve device according to any one of claims 1 to 5, characterized in that the abutment portions have a predetermined length from the edge portion toward the bent portion, and are inclined in a direction approaching each other or are parallel to each other as they extend toward the protruding side of the blade portion.

7. 7. The valve device according to claim 6, wherein the rim portion is pressed from the inner surface side to the outer surface side by 2n abutment portions that are configured by n blade portions and are arranged at equal intervals in the circumferential direction around the axis.

8. The blade portion is provided with a second plate portion extending from the end edge portion toward the inside of the leaf spring, The valve device according to claim 7, wherein the abutment portions have a predetermined length spanning the edge portions, and are inclined in a direction approaching each other or parallel to each other as they extend toward the protruding side of the blade portions.

9. A valve device comprising: a cylindrical guide portion; a moving member that moves along an axis of the guide portion; and a valve body that is connected to the moving member and controls a flow of a fluid, The movable member is provided with a seal portion that divides the space within the guide portion into a plurality of spaces, The seal portion includes an L-shaped packing that fits onto the inner surface of the guide portion, and a leaf spring that acts on the L-shaped packing, The L-shaped packing includes a plate-shaped base portion extending intersecting the axis, and a rim portion rising from an edge of the base portion and in sliding contact with an inner surface of the guide portion, the leaf spring includes a plate-shaped base plate portion disposed on the inner surface side of the base portion, and a plurality of blade portions provided to protrude radially from the base plate portion around the axis line, and which press the rim portion from the inner surface side to the outer surface side, thereby pressing the rim portion against the guide portion; the blade portion includes a bent portion that forms a boundary with the base portion, a plate portion that rises from the bent portion, and an edge portion that is provided on a tip side of the plate portion and abuts against the rim portion, Both widthwise ends and an edge portion connecting both widthwise ends on the outer surface side of the edge portion constitute abutment portions that abut on the rim portion, The valve device is characterized in that the curvature of the edge portion is substantially the same as the curvature of the inner surface of the rim portion.

10. A refrigeration cycle system equipped with a slide-type switching valve, 10. A refrigeration cycle system, wherein the slide-type switching valve is configured by the valve device according to claim 1 or 9.

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