Valve device and refrigeration cycle system

Abstract

The valve device and the refrigeration cycle system of the present application are less likely to be affected by temperature changes and can stably maintain sealing performance. A piston (50) of a cylindrical guide portion (10) of a valve device is provided with a seal portion (70) that divides the space inside the guide portion (10) into multiple spaces. The seal portion (70) includes an L gasket (80) and a leaf spring (90). The leaf spring (90) has a plate-shaped base plate portion (91) and multiple blade portions (92) that rise from the base plate portion (91) and press a rim portion (82) of the L gasket (80) against the guide portion (10) by pressing the rim portion (82) from the inner surface side to the outer surface side. The blade portion (92) has a first curved portion (93), a first blade portion (94), and a second curved portion (95). The width dimension of the first blade portion (94) decreases or remains the same from the first curved portion (93) side toward the second curved portion (95) side.

Description

Technical Field

[0001] This invention relates to a valve device and a refrigeration circulation system. Background Technology

[0002] A valve device for controlling the flow of fluid is known (for example, see Patent Document 1). As in Patent Document 1... Figure 2 As shown, the valve device described in Patent Document 1 includes a sealing portion 4 to limit fluid leakage. The sealing portion 4 is disposed within a guide portion 21 formed in a cylindrical shape, dividing the space within the guide portion 21 into one side along the X-axis and the other side along the X-axis. The sealing portion 4 includes an L-shaped gasket 45 consisting of an annular base 45a and a rim portion 45b erected on the outer peripheral edge of the base 45a. A leaf spring 41 is laminated on the inner surface side of the L-shaped gasket 45. The leaf spring 41 includes: a circular plate-shaped base plate portion 41a disposed on the inner surface side of the base 45a; and a blade portion 41b that rises from the base plate portion 41a and elastically deforms in the thickness direction. As in Patent Document 1… Figure 3 As shown, the two ends of the front end side of the blade portion 41b in the width direction form the endpoints P of the rim portion 45b. The endpoints P press the rim portion 45b outward by the elastic force after the elastic deformation of the blade portion 41b, and the tension of the pressed rim portion 45b makes the rim portion 45b fit tightly against the inner surface of the guide portion 21.

[0003] Existing technical documents

[0004] Patent documents

[0005] Patent Document 1: Japanese Patent Application Publication No. 2017-223293 Summary of the Invention

[0006] The problem that the invention aims to solve

[0007] However, the sealing part 4 described in Patent Document 1 is as follows: Figure 3As shown, the front end of the blade portion 41b is wider than the root end (i.e., the root end of the blade portion 41b is narrower). Therefore, if a sufficient number of blade portions 41b are configured to ensure sealing performance, the gap 41c between the blade portions 41b needs to be narrower than the width of the front end of the blade portion 41b. Consequently, multiple endpoints P are arranged at uneven intervals along the circumference of the base plate portion 41a. As a result, the contact state is unstable due to insufficient pressing on a part of the rim portion 45b, causing the rim portion 45b to float, which sometimes affects the sealing performance. Here, it is considered to reduce the width of the blade portion 41b to make the intervals between the endpoints P equal. However, in this case, the width of the root end of the blade portion 41b becomes evenly reduced, and the strength of the leaf spring 41 is easily reduced. This is not particularly preferable when the temperature of the operating environment is easily changed, such as changes in fluid temperature or changes in the temperature outside the valve device. Specifically, if the temperature of the sealing portion 4 decreases, the L-shield 45 contracts, and the rim portion 45b presses the blade portion 41b away from the inner surface of the guide portion 21, thereby sometimes applying a load to the front end side of the leaf spring 41. In this case, the width dimension of the blade portion 41b becomes smaller at the root side, where greater stress is generated than at the front end side, thus the strength at the root side is prone to becoming insufficient. Therefore, it is difficult to increase the overall design load of the leaf spring 41. Consequently, it is difficult to maintain the tension of the rim portion 45b, and it is difficult to maintain the sealing performance of the sealing portion 4.

[0008] The purpose of this invention is to provide a valve device and a refrigeration circulation system that are less susceptible to temperature changes and can stably maintain sealing performance.

[0009] Solution for solving the problem

[0010] To solve the aforementioned problems and achieve the objective, the valve device of the present invention is characterized by comprising: a cylindrical guide portion; a movable member that moves along the axis of the guide portion; and a valve core connected to the movable member and controlling the flow of fluid. The movable member is provided with a sealing portion that divides the space within the guide portion into multiple spaces. The sealing portion comprises: an L-shaped gasket that fits into the inner surface of the guide portion; and a leaf spring that acts on the L-shaped gasket. The L-shaped gasket comprises: a plate-shaped base that extends intersecting the axis; and a rim portion that rises from the edge of the base and is connected to the guide portion. The leaf spring has an inner surface sliding contact and includes: a plate-shaped base portion disposed on the inner surface side of the base portion; and a plurality of blade portions radially projecting from the base portion about the axis. The rim portion is pressed towards the guide portion by pressing the rim portion from the inner surface side to the outer surface side. Each blade portion includes: a curved portion forming a boundary with the base portion; a plate portion standing up from the curved portion; and an end edge portion disposed at the front end side of the plate portion and abutting against the rim portion. The width dimension of the plate portion decreases or remains the same from the curved portion side toward the end edge portion side.

[0011] According to this invention, the width of the plate portion decreases or remains the same from the curved portion side towards the end edge side, thereby easily reducing the width of the end edge portion that abuts against the rim portion. Therefore, the end edges can be easily arranged evenly in the circumferential direction around the axis. This suppresses insufficient local pressure on the rim portion, and the sealing performance of the seal portion can be stably maintained. Furthermore, in this structure, the width of the plate portion is larger or the same on the curved portion side than on the end edge side. Therefore, it is easy to ensure that the required strength on the curved portion side (blade root side), which generates greater stress when a load is applied from the rim portion to the blade portion via the end edge, can be appropriately borne by multiple blade portions. Therefore, the overall design load of the leaf spring can 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. Therefore, a valve device that is not easily affected by temperature changes and can stably maintain sealing performance can be provided.

[0012] Furthermore, it is preferable that the two ends of the plate portion in the width direction have straight portions that connect the curved portion to the end edge portion. With this structure, no special processing is required at the two ends of the plate portion in the width direction, simplifying the shape of the plate portion and thus reducing mold manufacturing costs, thereby enabling low-cost production of the sealing portion.

[0013] Alternatively, the plate portion may have two ends in the width direction comprising: a tapered portion that slopes toward each other towards the end edge; and a straight portion that is continuous with the end edge of the tapered portion and extends toward the end edge and is parallel to each other. With this structure, the width dimension of the blade portion is smaller on the straight portion side than on the tapered portion side, thus easily reducing the width dimension of the end edge portion that abuts against the rim portion. Therefore, the end edges can be easily arranged equally in the circumferential direction around the axis. Furthermore, in this structure, the width dimension of the blade portion is larger on the tapered portion side than on the straight portion side. Therefore, it is easy to ensure that the required strength of the tapered portion side (blade root side), which generates greater stress when a load is applied to the blade portion from the rim portion via the end edge, can be adequately borne by multiple blade portions. Therefore, the overall design load of the leaf spring can be increased, and the tension of the rim portion can be stably maintained even in environments where the seal expands or contracts due to temperature changes.

[0014] Alternatively, the plate portion may have curved portions at both ends in the width direction, which approach each other towards the end edge side. With this structure, the width dimension of the blade portion is smaller on the curved end edge side than on the curved side, thus easily reducing the width dimension of the end edge portion that abuts against the rim portion. Therefore, the end edges can be easily arranged equally in the circumferential direction around the axis. Furthermore, in this structure, the width dimension of the blade portion is larger on the curved side than on the curved end edge side. Therefore, it is easy to ensure that the required strength on the curved side (blade root side), which generates greater stress when a load is applied to the blade portion from the rim portion via the end edge, can be appropriately borne by multiple blade portions. Therefore, the overall design load of the leaf spring can be increased, and the tension of the rim portion can be stably maintained even in environments where the seal expands or contracts due to temperature changes.

[0015] Furthermore, preferably, an arcuate portion is provided at the edge of the base plate portion to connect the curved portions of adjacent blade portions to each other. This arcuate portion is formed in an arc shape protruding to a side opposite to the protrusion direction of the blade portion, where, with the radius of the arcuate portion being R and the thickness of the blade portion being t, t ≤ R ≤ 5t. With this structure, the radius of the arcuate portion can be minimized to approximately 5 times the thickness of the blade portion, making it easier for adjacent blade portions to approach each other. This increases the number of blade portions of the same circumference that can be formed on the base plate portion, distributing the load applied to the blade portions and further stabilizing the state of the blade portions pressing against the wheel rim portion. Furthermore, if the radius of the arcuate portion is too small, the management cost of the mold forming the leaf spring increases. However, according to this structure, by setting the radius of the arcuate portion to be greater than or equal to the thickness of the blade portion, the radius can be prevented from becoming too small, and the management cost of the mold can be appropriately maintained.

[0016] Furthermore, preferably, abutment portions that abut against the rim portion are provided at both ends of the blade portion in the width direction. These abutment portions have a predetermined length from the end edge toward the curved portion side and are inclined or parallel to each other in a direction approaching each other as they move toward the protruding side of the blade portion. With this structure, the abutment portions have a predetermined length from the end edge toward the curved portion side and are inclined or parallel to each other in a direction approaching each other as they move toward the protruding side of the blade portion. Therefore, as described below, the contact area between the blade portion and the rim portion can be increased, and the sealing performance of the sealing portion can be improved. That is, when comparing sealing components having a base plate portion of the same circumference, the same number of blade portions, and a rim portion of the same circumference, the structure where the abutment portions are inclined in a direction separating each other as they move toward the protruding side of the blade portion (for example, the structure in Patent Document 1 mentioned above) is superior. Figure 3 Compared to the blade portion 41b shown (hereinafter referred to as the conventional structure), the width dimension of the end edge portion (the second curved portion of the conventional structure) in this structure is smaller. Therefore, compared to the conventional structure, deformation between the two ends of the end edge portion (the second curved portion) in the width direction is more easily suppressed when force is applied between the abutting portions, allowing the abutting portion to reliably abut against the rim portion. Furthermore, in this structure, for example, when the rim portion is made of a easily deformable material such as resin, as described above, deformation of the end edge portion is suppressed, and it reliably abuts against the rim portion, thus allowing the end edge portion to sink deeper relative to the rim portion and make linear surface contact. Therefore, as described above, the contact area between the blade portion and the rim portion can be increased, improving the sealing performance of the sealing portion.

[0017] Furthermore, preferably, the rim portion is pressed from the inner surface side to the outer surface side by 2n abutment portions, each composed of n blade portions and arranged at equal intervals in the circumferential direction around the axis. With this structure, by arranging abutment portions in a number twice the number of blade portions in the circumferential direction, compared to a structure that uses a single point of the blade portion to press the rim portion, the equal gaps between the abutment portions can be further reduced, and the shape when multiple abutment portions are connected can approach a regular polygon. Therefore, the pressing of the rim portion is less likely to become locally insufficient, and the rim portion can be further suppressed from lifting off the inner surface of the guide portion.

[0018] Furthermore, preferably, a second plate portion extending from the end edge towards the inner side of the leaf spring is provided in the blade portion, and the abutment portion has a predetermined length spanning the end edge portion, and is inclined or parallel to each other in a direction of approaching each other as it moves toward the protruding side of the blade portion. With this structure, the abutment portion has a predetermined length spanning the end edge portion, and is inclined or parallel to each other in a direction of approaching each other as it moves toward the protruding side of the blade portion. Therefore, compared to the conventional structure described above, the width dimension of the end edge portion (the second curved portion in the conventional structure) of this structure is smaller. Therefore, compared to the conventional structure, it is easier to suppress deformation between the two ends of the end edge portion (the second curved portion) in the width direction when force is applied between the abutment portions, allowing the abutment portion to reliably abut against the rim portion. Furthermore, in this structure, for example, when the rim portion is made of a easily deformable material such as resin, as described above, deformation of the end edge portion is suppressed, and it reliably abuts against the rim portion, thus allowing the end edge portion to sink deeper into the rim portion and act as a linear surface contact. Therefore, as described above, the contact area between the blade portion and the wheel rim portion can be increased, thereby improving the sealing performance of the sealing portion.

[0019] Furthermore, the valve device of the present invention includes: a cylindrical guide portion; a moving member that moves along the axis of the guide portion; and a valve core connected to the moving member and controlling the flow of fluid. The moving member is characterized by having a sealing portion that divides the space within the guide portion into multiple spaces. The sealing portion includes: an L-shaped gasket that fits into the inner surface of the guide portion; and a leaf spring acting on the L-shaped gasket. The L-shaped gasket includes: a plate-shaped base portion extending intersecting the axis; and a rim portion that rises from the edge of the base portion and slides in contact with the inner surface of the guide portion. The leaf spring includes: a plate-shaped base portion disposed on the guide portion. The base portion has an inner surface side; and a plurality of blade portions that are radially arranged from the base plate portion about the axis. The rim portion is pressed towards the guide portion by pressing the rim portion from the inner surface side to the outer surface side. Each blade portion has: a curved portion that forms a boundary with the base plate portion; a plate portion that stands from the curved portion; and an end edge portion that is provided at the front end side of the plate portion and abuts against the rim portion. On the outer surface side of the end edge portion, the two ends in the width direction and the edge portion that connects the two ends in the width direction to each other form an abutting portion that abuts against the rim portion. The curvature of the edge portion is approximately the same as the curvature of the inner surface of the rim portion.

[0020] In structures where the two ends of the second curved portion are pressed towards the rim portion in the width direction, the pressing force on the rim portion between these two ends is sometimes insufficient. For example, in the leaf spring described in Patent Document 1, the front end side is wider than the root side, thus the spacing between the abutting portions of a single leaf portion tends to widen. Consequently, the pressing force on the rim portion between the abutting portions of a single leaf portion is particularly prone to becoming insufficient. Therefore, for example, when the rim portion shrinks (thermal deformation) due to a decrease in temperature, the rim portion may sometimes float towards the leaf portion between the two ends of the second curved portion, potentially causing fluid leakage. In this regard, according to this structure, in the leaf spring, the edge portion, whose curvature is set to be approximately the same as the curvature of the inner surface of the rim portion, is designated as the abutting portion, in addition to the two ends of the leaf portion in the width direction. Therefore, for each leaf portion, the contact area between the leaf portion and the rim portion can be increased efficiently and uniformly between the two ends of the leaf portion in the width direction, and the floating of the rim portion can be appropriately suppressed. Therefore, it is possible to provide a valve device that is not easily affected by temperature changes and can stably maintain sealing performance.

[0021] Furthermore, the refrigeration cycle system of the present invention includes a sliding switching valve, characterized in that the sliding switching valve is composed of the valve device described in any of the above claims. According to this structure, a refrigeration cycle system that is less susceptible to temperature changes and can stably maintain sealing performance can be provided.

[0022] Invention Effects

[0023] According to the present invention, a valve device and a refrigeration circulation system that are less susceptible to temperature changes and can stably maintain sealing performance can be provided. Attached Figure Description

[0024] Figure 1 This is a cross-sectional view of the electric valve of the first embodiment of the present invention cut along the axial direction of the guide portion.

[0025] Figure 2 It is Figure 1 The enlarged view of region A represents a section of it.

[0026] Figure 3 (A) is a cross-sectional view showing the state of the L-shaped gasket before deformation, and (B) is a cross-sectional view showing the state of the L-shaped gasket after deformation.

[0027] Figure 4 (A) is a three-dimensional view of the leaf spring, and (B) is a front view of the leaf spring with the leaf blades unfolded.

[0028] Figure 5 (A) is a perspective view of the leaf spring blade, which is part of the leaf spring, and (B) is a cross-sectional view of the leaf spring blade cut along its length.

[0029] Figure 6 This is an enlarged front view of a portion of a leaf spring with the blades extended.

[0030] Figure 7 It is magnification Figure 6 The front view of the blade section is shown.

[0031] Figure 8 (A) is a cross-sectional view showing the state of the leaf spring constituting the sealing part before deformation, and (B) is a cross-sectional view showing the state of the leaf spring after deformation.

[0032] Figure 9 (A) is a sectional view showing the leaf spring mounted on the guide section cut in a direction orthogonal to the axis of the guide section, and (B) is a front view showing the dimensional relationship of the leaf spring.

[0033] Figure 10 This is a conceptual diagram illustrating the refrigeration cycle system of the present invention.

[0034] Figure 11 (A) is a perspective view of a leaf spring according to a modified example of the first embodiment, and (B) is a view showing the leaf spring equipped with... Figure 11 (A) is a front view showing the dimensional relationships of the leaf spring's blade section, and (C) is a view with the blade section unfolded. Figure 11 (A) is a front view of the leaf spring with blade section shown.

[0035] Figure 12 (A) and (B) are cross-sectional views showing the changes in the leaf spring.

[0036] Figure 13 (A) is a front view of the leaf spring with the blade section unfolded in the second embodiment; (B) is a view of the leaf spring with the blade section unfolded. Figure 13 (A) is an enlarged front view of the main part.

[0037] Figure 14 (A) is a front view of the leaf spring with the blade section unfolded in the third embodiment; (B) is a view of the leaf spring with the blade section unfolded. Figure 14 (A) is an enlarged front view of the main part.

[0038] Figure 15 This is a cross-sectional view showing the leaf spring according to the fourth embodiment.

[0039] Figure 16 (A) is a front view of the leaf spring with the blade section unfolded in the fifth embodiment, and (B) is a perspective view of the leaf spring in the fifth embodiment.

[0040] Figure 17 It is Figure 16 (B) is an enlarged front view of the main part of the leaf spring. Detailed Implementation

[0041] The following is based on Figures 1-10 The first embodiment of the present invention will be described. In the following description, the extending direction of the axis L of the guide portion 10 described later will be referred to as the "axis L direction," one side of the axis L direction will be referred to as "one side L1," and the other side will be referred to as "the other side L2." Furthermore, the direction orthogonal (intersecting) with the axis L direction will be referred to as "radial X." In radial X, the side containing the axis L will be designated as the "inner side," and the side opposite to the inner side will be designated as the "outer side," for example, in... Figure 3 The inner and outer sides are also shown in the partial figures. The valve device of the first embodiment is, for example, a sliding four-way switching valve 100 (sliding switching valve) used in a refrigeration cycle system to switch the flow direction of fluid. The sliding 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 along the axis L. A D-port 11 extending radially X is formed on the side wall of the guide portion 10 by means of flanging or the like.

[0042] A D-connector pipe 11a, serving as a high-pressure piping, is fixed to port D11 via brazing or the like. One end of the D-connector pipe 11a is connected to the compressor 600 (described later). Figure 10 The guide section 10 is connected to the outlet, through which a high-pressure fluid such as refrigerant flows. On the inner surface 10a of the sidewall of the guide section 10, opposite to the D port 11, a plate-shaped valve seat component 20 extending along the axis L is provided. The radially X inner surface of the valve seat component 20 forms a valve seat surface 21 for sliding contact with the valve core 40 (described later). On the valve seat surface 21, from one side L1 to the other side L2, E ports 22, S ports 23, and C ports 24 are sequentially formed, extending radially X to the outer side of the guide section 10. E connector pipes 22a, S connector pipes 23a, and C connector pipes 24a, respectively, communicating with the inside and outside of the guide section 10, are connected to E ports 22, S ports 23, and C ports 24, and are fixed by brazing or the like. E connector pipes 22a, S connector pipes 23a, and C connector pipes 24a are piping for refrigerant flow, similar to D connector pipe 11a, and function as either high-pressure or low-pressure piping. One end of E-connector pipe 22a connects to the indoor heat exchanger 300 described later (see reference). Figure 10 Connect to the compressor 600 (see reference). One end of the S-connector pipe 23a is connected to the compressor 600 (see reference). Figure 10 The suction inlet of the C-connector pipe 24a is connected to the outdoor heat exchanger 500 (see below). Figure 10 )connect.

[0043] Cover members 30 are respectively installed at the openings at both ends of the guide portion 10 in the direction of axis L. The cover members 30 are made of metal and are formed into a roughly bowl shape with an inward opening in the direction of axis L. The cover members 30 are embedded in the mounting steps 12 formed by expanding the inner surface of both ends of the guide portion 10 in the direction of axis L, and are fixed by welding or the like. With the fixation of the cover members 30, 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 the piston 50 (moving member) described later: 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 tube 31 (capillary tube) is inserted through the wall of the cover member 30 disposed on one side L1. One end of the first working tube 31 communicates with the inside and outside of the first working chamber 14, and the other end communicates with the pilot valve 200 described later (see reference). Figure 10 The connection forms a flow path for the high-pressure or low-pressure working fluid to flow through, which drives the piston 50.

[0044] On the other hand, a cylindrical second working tube 32 (capillary tube) is inserted into the wall of the cover component 30 located on the other side L2. One end of the second working tube 32 communicates with the inside and outside of the second working chamber 16, and the other end is connected to the pilot valve 200 (see reference). Figure 10 The valve core 40 is connected to the piston 50 described later, forming a flow path that allows the working fluid to flow relative to the second working chamber 16. The valve core 40 includes a bowl-shaped portion 41 with a concave portion 41a opening towards the valve seat surface 21, and a flange portion 42 protruding outward from the opening edge of the concave portion 41a. The valve core 40 is connected to and held by the piston 50. The bottom surface of the flange portion 42 forms a sealing surface 43 that slides in contact with the valve seat surface 21. The sealing surface 43 is normally pressed towards the valve seat surface 21 by the pressure difference between the high-pressure chamber 15 and the E-connector pipe 22a, S-connector pipe 23a, or C-connector pipe 24a. Through this pressing, the valve core 40, while held in contact with the piston 50, can move back and forth along the axis L while the sealing surface 43 slides in contact with the valve seat surface 21.

[0045] The size of the opening of the concave portion 41a of the valve core 40 is set to cover the size of two adjacent openings among E port 22, S port 23, and C port 24. By setting this size, the valve core 40 moves forward and backward along the axis L, thereby switching the connection state of E port 22, S port 23, C port 24, and D port 11. Specifically, the concave portion 41a... Figure 1On the other side, at position L2, the S port 23 is internally connected to the C port 24, and the D port 11 is externally connected to the E port 22. In this state, high-pressure refrigerant flowing into the valve chamber 13 through the D connector pipe 11a and the D port 11 flows towards the valve seat component 20 through the equalizing hole 62 (described later), and flows to the E connector pipe 22a via the E port 22, which is not covered by the concave portion 41a. On the other hand, low-pressure refrigerant flowing into the concave portion 41a through the C connector pipe 24a and the C port 24 flows to the S connector pipe 23a via the S port 23.

[0046] Conversely, when the valve core 40 moves from position L2 on one side to position L1 on the other side (not shown), the concave portion 41a internally connects port E22 and port S23, and externally connects port D11 and port C24. In this state, high-pressure refrigerant flowing into the valve chamber 13 through port D11 and connector D1a flows through the equalizing hole 62 to the valve seat component 20 side, and flows to connector C24a via port C24, which is not covered by the concave portion 41a. On the other hand, low-pressure refrigerant flowing into the concave portion 41a through port E22 and connector E22 flows to connector S23a via port S23. Thus, the flow of fluid is controlled by the forward and backward movement of the valve core 40 along the axis L.

[0047] A piston 50 (moving member) that moves along axis L is disposed inside the valve housing 1. The piston 50 has a connecting member 60 that holds the valve core 40. The connecting member 60 is formed by bending or otherwise shaping a metal material such as stainless steel, and is formed into a plate shape extending along axis L. An elongated oval valve core holding hole 61 extending in the plate thickness direction (radial X) is formed at the center of the connecting member 60. The cup-shaped portion 41 of the valve core 40 is inserted into the valve core holding hole 61 and held in this state. That is, the valve core 40 is connected to the piston 50. A circular pressure equalization hole 62 extending in the plate thickness direction (radial X) is formed on one side L1 and the other side L2 of the valve core holding hole 61. The pressure equalization hole 62 connects the D port 11 side of the high pressure chamber 15 to the valve seat member 20 side of the high pressure chamber 15. The two ends of the connecting component 60 in the direction of axis L are bent outward in the radial direction X, and a sealing part 70 is installed on the outer surface of the bent part in the direction of axis L.

[0048] The sealing part 70 is a partition that divides the valve chamber 13 into a first working chamber 14, a high-pressure chamber 15, and a second working chamber 16 (divided into multiple spaces), such as... Figure 2 As shown, it includes a first reinforcing member 71, a second reinforcing member 72, an L-shaped gasket 80, and a leaf spring 90. Additionally, in Figure 2The structure of the sealing portion 70 disposed on the other side L2 within the valve chamber 13 is shown. The structure of the sealing portion 70 disposed on one side L1 is the same, therefore a detailed description and illustration of the sealing portion 70 on one side L1 are omitted. The first reinforcing member 71 is a plate member disposed on one side L1 of the leaf spring 90, and is formed into a circular plate with an outer diameter approximately the same as that of the base plate portion 91 of the leaf spring 90. A rivet hole 71a extending along the axis L and a threaded hole (not shown) are formed in the first reinforcing member 71. The second reinforcing member 72 is a plate member disposed on the other side L2 of the L gasket 80, and is formed into a circular plate with an outer diameter larger than that of the base portion 81 of the L gasket 80.

[0049] The second reinforcing member 72 reinforces the sealing portion 70 and also functions as a limiting portion to restrict the movement of the piston 50 by abutting against the opening edge of the cover member 30 within the guide portion 10. The second reinforcing member 72 has a rivet hole 72a extending along the axis L and a threaded hole (not shown). The L-shield 80 is constructed using, for example, a resin material such as Teflon (registered trademark), an elastomer, or rubber, and has a base 81 extending radially X and a rim portion 82 rising from the edge of the base 81 inwards along the axis L. The base 81 is formed in a circular plate shape and extends orthogonally to the axis L. Figure 1 As shown, a threaded hole 83 and a rivet hole 84 are formed on the plate surface of the base 81, which are through along the axis L (plate thickness direction).

[0050] The rim portion 82 is formed by expanding its diameter in a manner that extends inward toward the axis L and outward toward the radial X direction, enabling it to elastically deform in the radial X (plate thickness direction). For example... Figure 3 As shown in (A), the outer surface 82a of the front end side of the wheel rim portion 82 before elastic deformation is located outside the inner surface 10a of the sidewall of the guide portion 10 shown by the imaginary line. That is, the outer diameter of the front end side of the wheel rim portion 82 before elastic deformation is larger than the inner diameter of the guide portion 10. Furthermore, when the sealing portion 70 is provided in the guide portion 10, as... Figure 3 As shown in (B), the rim portion 82 elastically deforms inward to reduce its diameter, fitting into the inner surface 10a of the sidewall of the guide portion 10. In this state, the outer surface 82a of the rim portion 82 can slide in contact with the inner surface 10a of the guide portion 10.

[0051] The leaf spring 90 is a component used to press the L-pad 80 towards the guide portion 10 by acting on it, and is made of metal. The leaf spring 90 has a circular plate-shaped base plate portion 91 extending radially X. The base plate portion 91 is disposed in a stacked state on the inner surface side of the base portion 81 of the L-pad 80 (in... Figure 3 (B) is L1 on one side. For example... Figure 4As shown in (A), a threaded hole 91a and a rivet hole 91b extending along the axial direction L (thickness direction) are formed on the surface of the substrate portion 91. Multiple blade portions 92 are formed on the outer periphery of the substrate portion 91. Figure 4 As shown in (B), the blade portion 92 is arranged radially with the axis L as the center, as... Figure 4 As shown in (A), the front end is bent from the substrate 91 by starting from the boundary with the substrate 91.

[0052] In this embodiment, a total of 24 blade portions 92 are formed at equal intervals around the axis L, but the number of blade portions 92 and the spacing between adjacent blade portions 92 can be appropriately changed. For example... Figure 5 As shown in (A), the blade portion 92 includes a first curved portion 93 (curved portion) forming the boundary with the base plate portion 91 and a first blade portion 94 (plate portion) rising from the first curved portion 93. Furthermore, the blade portion 92 includes a second curved portion 95 (end edge portion) disposed at the front end side of the first blade portion 94; and a second blade portion 96 (second plate portion) extending radially inward (inner side of the leaf spring 90) from the second curved portion 95. The first curved portion 93 is formed with an arc-shaped R-shape on both its inner and outer surfaces, and is formed near the outer peripheral edge of the base plate portion 91, which is formed into a circular plate shape as described above. However, it is not limited to this; for example, a radially outward protrusion may be formed in advance at the location where the blade portion 92 is formed on the outer peripheral edge of the base plate portion 91, and the first curved portion 93 may be formed at the protruding end edge of this protrusion. That is, it may not be a circular plate shape, but rather the first curved portion 93 may be formed on the base plate portion 91 in a shape where the protrusion protrudes from a circular plate.

[0053] The first blade portion 94 is formed in a flat plate shape, and its width decreases as it moves from the first curved portion 93 side toward the second curved portion 95 side. Additionally, as... Figure 5 As shown in (B), the first blade portion 94 extends obliquely outward in a manner that it is located radially X-outward toward one side L1. Figure 5 As shown in (A), the two ends of the first blade portion 94 extend in a straight line from the first curved portion 93 toward the second curved portion 95 in the width direction, forming a straight portion connecting the first curved portion 93 and the second curved portion 95. The second curved portion 95 is formed by bending one side L1 (front end side) of the blade portion 92 radially inward, forming the end edge of the first blade portion 94 and the boundary between the first blade portion 94 and the second blade portion 96. Figure 5 As shown in (B), the second blade portion 96 extends from the second curved portion 95 toward a side L1 that is radially inward than the extending direction of the first blade portion 94. Figure 6As shown, abutment portions 97 that abut against the rim portion 82 are respectively provided at both ends of the blade portion 92 in the width direction. The abutment portions 97 extend across the second curved portion 95 and have a predetermined length from the first blade portion 94 to the second blade portion 96.

[0054] like Figure 7 As shown, the abutment portion 97 extends between a first imaginary line b1 and a second imaginary line b2, which are approximately orthogonal to an imaginary radial line a1 relative to the central portion of the front end of the blade portion 92, connecting the axis L. The abutment portion 97 tilts towards each other as it protrudes toward the protruding side of the blade portion 92. Thus, the abutment portion 97 extends intersecting with the imaginary line a2 extending radially from the axis L. The blade portion 92 configured in this way can elastically deform in the radial direction X, starting from the first bending portion 93. Figure 8 As shown in (A), in the leaf portion 92 before elastic deformation, the outer surface portion 97a of the abutment portion 97 is located radially outward from the abutted portion 82b, which is the abutment target in the rim portion 82 before deformation, as shown by the imaginary line. That is, the outer diameter of the portion of the leaf spring 90 having the abutment portion 97 is larger than the inner diameter of the portion of the rim portion 82 having the abutted portion 82b. Furthermore, when assembling the sealing portion 70, as... Figure 8 As shown in (B), the abutting portion 97 of the blade portion 92 elastically deforms inward in the radial direction X to reduce its diameter, and sinks and abuts against the abutting portion 82b of the wheel rim portion 82 in the plate thickness direction.

[0055] Furthermore, as described above, since at least a portion of both ends of the blade portion 92 in the width direction is designated as abutment portions 97, when the blade portion 92 provided on the leaf spring 90 is provided as n pieces, 2n abutment portions 97 are provided on the leaf spring 90. Figure 9 As shown in (A), in this embodiment, a total of 24 blades are formed in the blade portion 92, therefore a total of 48 contact portions 97 are provided. Figure 9 As shown in (B), the plurality of blade portions 92 thus formed are connected by an arcuate portion 91c formed on the edge of the substrate portion 91. The arcuate portion 91c is formed by making an arcuate cut on the edge of the substrate portion 91 that is convex to the side opposite to the protruding direction of the blade portion 92, and the first curved portions 93 of adjacent blade portions 92 are connected to each other.

[0056] Furthermore, if the radius of the arc portion 91c is increased, the spacing between adjacent blade portions 92 widens, making it difficult to set a large number of blade portions 92 within a substrate portion 91 of the same circumference. Therefore, from the viewpoint 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 cost of the mold forming the leaf spring 90 increases. Therefore, from the viewpoint 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 size. Specifically, as... Figure 9 As shown in (B), when the radius of the arc portion 91c is set to R and the thickness of the blade portion 92 is set to t, it is preferable to set t ≤ R ≤ 5t. With this structure, the radius R of the arc portion 91c can be made to converge to approximately 5 times the thickness t of the blade portion 92, making it easier for adjacent blade portions 92 to be relatively close. On the other hand, by setting the radius R of the arc portion 91c to be greater than or equal to the thickness t of the blade portion 92, it is possible to prevent the radius R from becoming too small, thus maintaining reasonable mold management costs.

[0057] The L-shaped gasket 80, leaf spring 90, first reinforcing member 71, and second reinforcing member 72 thus formed are integrated by rivets 73 and fixed to both ends of the connecting member 60 along the L-axis by bolts 74. Specifically, as... Figure 2 As shown in (A), the first reinforcing member 71, leaf spring 90, L-shield 80, and second reinforcing member 72 are stacked sequentially from one side L1 to the other side L2. In this state, the first reinforcing member 71, leaf spring 90, L-shield 80, and second reinforcing member 72 are fixed by rivets 73 inserted into rivet holes 71a, rivet holes 91b, rivet holes 84, and rivet holes 72a. The sealing part 70 is fixed to the connecting member 60 by bolts 74. Specifically, the sealing part 70 is fixed to both ends of the connecting member 60 along the axis L direction by bolts 74 inserted into threaded holes (not shown) of the first reinforcing member 71, the leaf spring 90, the L-shield 80, and the second reinforcing member 72. The L-shield 80 of the sealing part 70, which is integral with the connecting member 60, is disposed within the guide part 10. The L-shaped gasket 80 disposed within the guide portion 10 fits into the inner surface 10a of the side wall of the guide portion 10.

[0058] When the L-shield 80 is engaged, the leaf spring 90's blade portion 92 is pressed against the rim portion 82, which deforms radially inward, and elastically deforms radially inward. Furthermore, the force by which the leaf portion 92 attempts to return to its pre-elastic deformation state is applied via the abutment portion 97, pressing the rim portion 82 from the inner surface side to the outer surface side. Through this pressing, the rim portion 82 is pressed against the inner surface 10a of the guide portion 10. Additionally, the force by which the rim portion 82 itself attempts to return to its pre-elastic shape state is applied, pressing the rim portion 82 against the inner surface 10a of the guide portion 10. Through these pressings, the sealing portion 70 and the guide portion 10 are sealed, limiting fluid leakage between the first chamber 14, the high-pressure chamber 15, and the second chamber 16. At this time, as... Figure 9 As shown in (A), the blade portion 92 is arranged at equal intervals in the circumferential direction around the axis L, thereby suppressing the deviation of the pressing force of the pressing wheel portion 82.

[0059] Here, for example, as in the leaf spring described in Patent Document 1 above, in a structure where the width of the leaf portion increases from the root side to the front side, it is easy to become as follows. That is, in Patent Document 1... Figure 2 , Figure 3 When a load is applied to the front end of the blade portion 41b due to deformation of the rim portion 45b, the width of the root side of the blade portion 41b, which generates greater stress, becomes narrower. Therefore, the strength at the root side becomes insufficient, and the overall design load of the leaf spring 41 tends to decrease. Furthermore, in this structure, the distance between the two endpoints P (abutment portions) of one blade portion 41b and the distance between the endpoint P of one blade portion 41b and the endpoint P of another adjacent blade portion 41b tends to decrease. Consequently, it is difficult to evenly arrange the multiple endpoints P around the axis L in the circumferential direction, and the pressing force on the rim portion 45b tends to be offset. Moreover, to eliminate this offset in pressing force, the leaf spring 41 and the entire electric valve need to be enlarged.

[0060] Furthermore, the second curved portion 41b2 (second curved portion) is formed, and the endpoint P is prone to point contact when it abuts against the rim portion 45b. Therefore, it is difficult to increase the contact area between the blade portion 41b and the rim portion 45b, and it is difficult to improve the sealing performance of the sealing portion 4. Moreover, the rim portion 45b, which is the abutment destination of the endpoint P, is formed into a cylindrical shape along the inner circumference of the guide portion 21, so the inner surface of the rim portion 45b that directly abuts against the endpoint P is arc-shaped. In this case, the blade portion 41b includes the endpoint P at both ends in the width direction and extends along a radial line centered on the axis X, so the leading corner of the blade portion 41b is prone to interfere with the rim portion 45b.

[0061] In contrast, in the first embodiment, such as Figure 9 As shown in (B), the width dimension W2 of the second curved portion 95 of the blade portion 92 is set to be smaller than the width dimension W1 (root width) of the first curved portion 93 of the blade portion 92. With this setting, the required strength can be easily ensured on the side of the first curved portion 93, which generates greater stress. As a result, the load mentioned above can be properly borne by multiple blade portions 92, and the overall design load of the leaf spring 90 is increased. In addition, by making the width dimension W2 smaller than the width dimension W1, the following becomes easier. That is, without making the leaf spring 90 larger, it is easy to set the interval S1 (interval width) between the abutting portions 97 of one blade portion 92 and the interval S2 (gap width) between the abutting portions 97 of one blade portion 92 and the abutting portions 97 of another adjacent blade portion 92 to be approximately the same. Therefore, it is possible to avoid making the leaf spring 90 larger, and to suppress the local insufficiency of the pressing pressure on the rim portion 82, thus stably maintaining the sealing performance of the sealing portion 70.

[0062] Furthermore, the relationship between the aforementioned interval S1 (width of the contact portion) and interval S2 (gap width) is preferably 0.8 ≤ S1 / S2 ≤ 1.2, and more preferably S1 = S2. Additionally, as described above, in the first embodiment, the contact portion 97 is inclined in a direction of mutual approach as it protrudes toward the protruding side of the blade portion 92. Therefore, as described below, the contact area between the blade portion 92 and the rim portion 82 can be increased, and the sealing performance of the sealing portion 70 can be improved. That is, when comparing sealing members 70 having the same circumference of the base plate portion 91, the same number of blade portions 92, and the same circumference of the rim portion 82, the structure in which the contact portion 97 is inclined in a direction of mutual separation as it protrudes toward the protruding side of the blade portion 92 (for example, the structure described in Patent Document 1 above) is superior. Figure 3 Compared to the conventional structure (shown as blade portion 41b, hereinafter referred to as the existing structure), the width dimension W2 of the second curved portion 95 in this embodiment is smaller. Therefore, compared to the conventional structure, it is easier to suppress deformation between the two ends of the second curved portion 95 in the width direction when force is applied between the abutting portions 97, allowing the abutting portions 97 to reliably abut against the rim portion 82. Furthermore, at this time, the abutting portion 97 can be deeply recessed into the rim portion 82 while maintaining a linear surface contact. Therefore, as described above, the contact area between the blade portion 92 and the rim portion 82 can be increased, improving the sealing performance of the sealing portion 70. In addition, in this structure, the two ends of the blade portion 92, including the abutting portion 97, do not extend along a radial line centered on the axis L, making it difficult for the leading corner of the second blade portion 96 to interfere with the inner surface of the rim portion 82. This further stabilizes the state in which the blade portion 92 presses against the rim portion 82.

[0063] Next, the operation of the sliding four-way switching valve 100 will be explained. For example... Figure 10 As shown, the sliding four-way switching valve 100, for example, together with the compressor 600, indoor heat exchanger 300, throttling device 400, and outdoor heat exchanger 500, constitutes a refrigeration cycle system. Furthermore, the working fluid controlled by the pilot valve 200 drives the piston 50 to switch the flow path of fluids such as refrigerant, switching between heating and cooling states. For example, in heating state, as... Figure 10 As shown, high-pressure working fluid, controlled by 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. Therefore, due to the pressure difference between the first and second working chambers 14 and 16, piston 50 moves to the other side L2. Furthermore, the movement of piston 50 stops when the second reinforcing member 72 on the other side L2 abuts against the opening edge of the cover member 30 on the other side L2. Thus, as... Figure 10As shown, valve core 40 is located at position L2 on the other side. In this state, the high-pressure refrigerant flowing from the discharge port of compressor 600 flows in the following sequence: D connector pipe 11a, D port 11, D port 11 side of valve chamber 13, equalizing hole 62, valve seat component 20 side of valve chamber 13, E port 22, E connector pipe 22a, indoor heat exchanger 300, and throttling device 400. Meanwhile, the low-pressure refrigerant flowing from outdoor heat exchanger 500 flows in the following sequence: C connector pipe 24a, C port 24, concave portion 41a, S port 23, S connector pipe 23a, and suction port of compressor 600.

[0064] On the other hand, in the cooling state, the high-pressure working fluid controlled by the pilot valve 200 flows into the second working chamber 16 via the second working capillary tube 32. Meanwhile, the low-pressure working fluid flows into the first working chamber 14 via the first working capillary tube 31. Thus, due to the pressure difference between the first working chamber 14 and the second working chamber 16, the piston 50 moves to one side L1. Furthermore, the movement of the piston 50 stops when the second reinforcing member 72 of one side L1 comes into contact with the opening edge of the cover member 30 of one side L1. As a result, the valve core 40 is located at the position of one side L1 (not shown). In this state, the high-pressure refrigerant flowing from the discharge port of the compressor 600 flows in the following sequence: D-connector pipe 11a, D-port 11, the D-port 11 side of the valve chamber 13, the equalizing hole 62, the valve seat member 20 side of the valve chamber 13, the C-port 24, the C-connector pipe 24a, the outdoor heat exchanger 500, and the throttling device 400. Furthermore, the low-pressure refrigerant flowing from the indoor heat exchanger 300 flows in the following order: E-connector pipe 22a, E-port 22, concave portion 41a, S-port 23, S-connector pipe 23a, and the suction port of the compressor 600. Moreover, when the piston 50 is driven in this manner, the sealing portion 70 maintains a seal between the piston 50 and the valve housing 1, limiting fluid leakage between the first working chamber 14, the high-pressure chamber 15, and the second working chamber 16.

[0065] Next, a variation of the first embodiment will be described. Figure 11 (A) is a perspective view of the leaf spring 90A of a modified example of the first embodiment. Figure 11 (B) indicates possession Figure 11 (A) is a front view showing the dimensional relationship of the leaf spring 90A of the blade portion 92A. Figure 11 (C) is an expansion Figure 11 (A) shows a front view of the leaf spring 90A of the blade section 92A. (See diagram below.) Figure 11 As shown in (A), in the modified example, the shape of the blade portion 92A differs from that in the first embodiment. Specifically, as... Figure 11As shown in (B), the width dimension of the first blade portion 94A (plate portion) is the same from the first curved portion 93A (curved portion) side towards the second curved portion 95A (end edge portion). That is, the second curved portion 95A of the blade portion 92A and the first curved portion 93A of the blade portion 92A have the same width dimension W3. Moreover, as Figure 11 As shown in (C), the width dimension of the blade portion 92 having the abutment portion 97A is the same toward the second blade portion 96 (second plate portion). According to this modified example, it is easy to keep the stress generated on the first curved portion 93A side and the second curved portion 95A side of the blade portion 92A constant, and the set load of the leaf spring 90A can be increased.

[0066] According to the first embodiment and its variations described above, the width dimension of the first blade portion 94 (first blade portion 94A) decreases or remains the same from the first curved portion 93 (first curved portion 93A) side toward the second curved portion 95 (second curved portion 95A) side, thereby easily reducing the width dimension of the second curved portion 95 that abuts against the rim portion 82. Therefore, the second curved portions 95 can be easily and evenly arranged in the circumferential direction around the axis L. This suppresses insufficient pressing on the rim portion 82, and the sealing performance of the sealing portion 70 can be stably maintained. Furthermore, in this structure, the width dimension of the first blade portion 94 is larger or the same on the first curved portion 93 side than on the second curved portion 95 side. Therefore, it is easy to ensure that the required strength on the first curved portion 93 side (blade root side), which generates greater stress when a load is applied from the rim portion 82 to the blade portion 92 (blade portion 92A) via the second curved portion 95, can be appropriately borne by the plurality of blade portions 92. Therefore, the overall design load of the leaf spring 90 (leaf spring 90A) can be increased, and the tension of the rim portion 82 can be stably maintained even when the sealing portion 70 expands or contracts due to temperature changes. Therefore, a sliding four-way switching valve 100 (valve device) that is not easily affected by temperature changes and can stably maintain sealing performance can be provided.

[0067] Furthermore, according to the first embodiment and its variations, the two ends of the first blade portion 94 of the leaf spring 90 in the width direction are formed as straight portions connecting the first curved portion 93 and the second curved portion 95. With this structure, no special processing is required on the two ends of the first blade portion 94 in the width direction, and the shape of the first blade portion 94 can be simplified. Therefore, mold manufacturing costs can be reduced, and the sealing portion 70 can be manufactured at a low cost.

[0068] Furthermore, according to the first embodiment and its variations, when the radius of the arc portion 91c of the leaf spring 90 is set to R and the thickness of the blade portion 92 is set to t, t ≤ R ≤ 5t holds true. With this structure, the radius R of the arc portion 91c can be maximized to approximately 5 times the thickness t of the blade portion 92, making it easier for adjacent blade portions 92 to approach each other. This increases the number of blade portions 92 of the same circumference that can be formed on the substrate portion 91, dispersing the load applied to the blade portions 92 and further stabilizing the state of the blade portions 92 pressing against the wheel rim portion 82. Moreover, if the radius R of the arc portion 91c is too small, the management cost of the mold forming the leaf spring 90 increases. However, according to this structure, by setting the radius R of the arc portion 91c to be greater than or equal to the thickness t of the blade portion 92, the radius R can be prevented from becoming too small, and the management cost of the mold can be appropriately maintained.

[0069] Furthermore, according to the first embodiment and its variations, the abutment portion 97 (abutment portion 97A) has a predetermined length, extending across the second curved portion 95, and is inclined or parallel towards each other as it protrudes toward the protruding side of the blade portion 92. Therefore, as described above, when comparing sealing portions 70 with substrate portions 91 having the same circumference, the same number of blade portions 92, and rim portions 82 having the same circumference, it is easier to suppress deformation between the two ends of the second curved portion 95 in the width direction when force is applied between the abutment portions 97 compared to conventional structures. Therefore, the abutment portion 97 can be made to sink deeper into the rim portion 82 while maintaining a linear surface contact. Therefore, the contact area between the blade portion 92 and the rim portion 82 can be increased, and the sealing performance of the sealing portion 70 can be improved.

[0070] Furthermore, according to the first embodiment and its variations, by arranging twice the number of abutment portions 97 evenly along the circumference, the uniform gap between the abutment portions 97 can be further reduced compared to a structure that uses a single point of the blade portion 92 to press the rim portion 82. Therefore, the shape can be made close to a regular polygon when multiple abutment portions 97 are connected. Consequently, the pressing of the rim portion 82 is less likely to become inadequate locally, and the rim portion 82 can be further suppressed from lifting off the inner surface of the guide portion 10.

[0071] Furthermore, according to the first embodiment and its variations, a refrigeration cycle system that is difficult to be affected by temperature changes and can stably maintain sealing performance can be provided.

[0072] Furthermore, in the first embodiment and its variations, the blade portion 92 (blade portion 92A) of the leaf spring 90 (leaf spring 90A) is composed of the first curved portion 93 (first curved portion 93A), the first blade portion 94 (first blade portion 94), the second curved portion 95 (second curved portion 95A), and the second blade portion 96. However, the structure of the blade portion 92 is not limited to this. Figure 12 (A) and (B) are sectional views showing the 90° change in the leaf spring. For example... Figure 12 As shown in (A), the leaf spring 90 has a third bend α1 between the first bend 93 and the second bend 95, and a fourth bend α2 on the second blade portion 96. The third bend α1 and the fourth bend α2 are the starting points for bending the blade portion 92 toward the inside of the leaf spring 90. Furthermore, additional bends such as the third bend α1 and the fourth bend α2 can be added as a fifth bend, a sixth bend, etc. Thus, in the blade portion 92, multiple bends other than the first bend 93 and the second bend 95 can be provided between the first bend 93 and the second bend 95, or on the side closer to the second blade portion 96 than the second bend 95. Additionally, as... Figure 11 As shown in (B), the first blade portion 94 does not necessarily need to be formed as a flat plate, but can also be formed curved toward the outside of the leaf spring 90, with its plate surface becoming a curved surface β.

[0073] Next, the second embodiment of the present invention will be described. Figure 13 (A) is a front view of the leaf spring 90B after the blade portion 92B has been unfolded in the second embodiment. Figure 13 (B) is to Figure 13 (A) is a magnified front view of the main part. (See diagram below.) Figure 13 As shown in (A), in the second embodiment, the shape of the blade portion 92B differs from the shapes of the blade portions 92 and 92A described above. Specifically, as... Figure 13 As shown in (B), the two ends of the first blade portion 94B (plate portion) in the width direction do not form straight portions, but are composed of a tapered portion 98a on the side of the first curved portion 93B (curved portion) and a straight portion 98b on the side of the second curved portion 95B (end edge portion). The tapered portion 98a is inclined in a direction that approaches each other as it moves toward the side of the second curved portion 95B. The straight portion 98b is continuous with the second curved portion 95B side of the tapered portion 98a and is parallel to each other toward the side of the second curved portion 95B.

[0074] With this structure, the width of the blade portion 92B is smaller on the straight portion 98b side than on the tapered portion 98a side, thus easily reducing the width of the second curved portion 95B that abuts against the rim portion 82. Therefore, the second curved portions 95B can be easily arranged evenly in the circumferential direction around the axis L. Furthermore, in this structure, the width of the blade portion 92B is larger on the tapered portion 98a side than on the straight portion 98b side. Therefore, it is easy to ensure that the required strength of the tapered portion 98a side (blade root side), which generates greater stress when a load is applied to the blade portion 92B from the rim portion 82 via the second curved portion 95B, can be appropriately borne by the multiple blade portions 92B. Therefore, the overall design load of the leaf spring 90B can be increased, and the tension of the rim portion 82 can be stably maintained even when the sealing portion 70 expands or contracts due to temperature changes.

[0075] Next, the third embodiment of the present invention will be described. Figure 14 (A) is a front view of the leaf spring 90C after the blade portion 92C is unfolded in the third embodiment. Figure 14 (B) is to Figure 14 (A) is a magnified front view of the main part. (See diagram below.) Figure 14 As shown in (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... Figure 14 As shown in (B), the two ends of the first blade portion 94C (plate portion) in the width direction do not form straight sections, but are instead composed of curved sections 99. The curved sections are formed as smooth curves that approach each other towards the second curved section 95C (end edge portion). Furthermore, Figure 14 (B) The curved section 99 shown is elliptical, but it is not limited to this. It can also be formed in various curved shapes such as a single R shape or a parabola shape.

[0076] With this structure, the width dimension of the blade portion 92C is smaller on the side of the second curved portion 95C of the curve portion 99 than on the side of the first curved portion 93C, thus making it easier to reduce the width dimension of the second curved portion 95C that abuts against the rim portion 82. Therefore, it is easy to arrange the second curved portions 95C equally in the circumferential direction around the axis L. In addition, in this structure, the width dimension of the blade portion 92C is larger on the side of the first curved portion 93C of the curve portion 99 than on the side of the second curved portion 95C. Therefore, it is easy to ensure that the required strength of the side of the first curved portion 93C (blade root side), which generates greater stress when a load is applied to the blade portion 92C from the rim portion 82 via the second curved portion 95C, can be properly borne by the multiple blade portions 92C. Therefore, the overall design load of the leaf spring 90C can be increased, and the tension of the rim portion 82 can be stably maintained even in an environment where the sealing portion 70 expands or contracts due to temperature changes.

[0077] Next, the fourth embodiment of the present invention will be described. Figure 15 This is a cross-sectional view showing the leaf spring 90D according to the fourth embodiment. (Example) Figure 15 As shown, in the fourth embodiment, the shape of the blade portion 92D differs from that of blade portions 92, 92A, 92B, and 92C. Specifically, the blade portion 92D has an end edge portion 95D corresponding to the second curved portion 95 at the leading end of the first blade portion 94D. Furthermore, the second blade portion 96 is omitted in the blade portion 92D. In this blade portion 92D, the width dimension of the first blade portion 94D decreases or remains the same from the first curved portion 93D (curved portion) side toward the end edge portion 95D side.

[0078] Moreover, such as Figure 15 As shown, abutment portions 97D are respectively provided at both ends of the blade portion 92D in the width direction. The abutment portions 97D are equivalent to the abutment portions 97 described above. Although detailed illustrations are omitted, the abutment portions 97D have a predetermined length from the end edge portion 95D to the first curved portion 93D side, and are inclined or parallel to each other in a direction of approaching each other as they move toward the protruding side of the blade portion 92D. According to this fourth embodiment, as described above, when comparing the sealing portions 70 having the same circumference of the base plate portion 91D, the same number of blade portions 92D, and the same circumference of the rim portion 82, it is easier to suppress the deformation between the two ends of the end edge portion 95D in the width direction when force is applied between the abutment portions 97D compared to conventional structures. Therefore, the abutment portions 97D can be made to sink deeper into the rim portion 82 while making linear surface contact. Therefore, the contact area between the blade portion 92D and the rim portion 82 can be increased, and the sealing performance of the sealing portion 70 can be improved.

[0079] Next, the fifth embodiment of the present invention will be described. Figure 16 (A) is a front view of the leaf spring 90E after the blade portion 92E has been unfolded in the fifth embodiment. Figure 16 (B) is a perspective view of the leaf spring 90E according to the fifth embodiment. Figure 17 It is Figure 16 (B) is an enlarged front view of the main part of the leaf spring 90E. Figure 16 As shown in (A), in the fifth embodiment, the shape of blade portion 92E differs from that of blade portions 92, 92A, 92B, 92C, and 92D. Specifically, as... Figure 16 As shown in (A) and (B), the width of the blade portion 92E increases from the first curved portion 93E (curved portion) side towards the second curved portion 95E (end edge portion). With this shape, the number of blades formed in the blade portion 92E of the leaf spring 90E is 18. Furthermore, as... Figure 17 As shown, on the outer surface side of the second curved portion 95E, the edge portion 95f that connects the two ends 95d of the second curved portion 95E in the width direction is formed into an arc shape.

[0080] The curvature of the edge portion 95f is set to be 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 pressing the rim portion 82. Furthermore, the two ends 95d in the width direction of the second curved portion 95E and the edge portion 95f constitute the abutment portion 97E of the fifth embodiment. Here, as described above, particularly in the structure where the two ends in the width direction of the second curved portion 95 are pressed against the rim portion 82, sometimes the pressing force on the rim portion 82 between these two ends is insufficient.

[0081] This is readily apparent in valve devices, such as those described in Patent Document 1 above. Specifically, in Patent Document 1... Figure 2 , Figure 3 In the leaf spring shown, the front end of the leaf spring 41b is wider than the root end, thus the distance between the endpoints P of a leaf spring 41b tends to widen. Consequently, the pressing force on the rim portion 45b between the endpoints P of a leaf spring 41b becomes particularly insufficient. In this case, for example, when the rim portion 45b shrinks due to temperature decrease (thermal deformation), the rim portion 45b may sometimes float towards the leaf spring 41b between the endpoints P, potentially causing fluid leakage.

[0082] Regarding this, in the leaf spring 90E of the fifth embodiment, except for the two ends 95d in the width direction of the blade portion 92E, the edge portion 95f, which is set to have a curvature 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 sidewall of the guide portion 10, becomes the abutment portion 97E. Therefore, regarding each blade portion 92E, the contact area between the blade portion 92E and the rim portion 82 can be increased efficiently and uniformly between the two ends 95d, and the lifting of the rim portion 82 can be appropriately suppressed. Therefore, a sliding four-way switching valve 100 that is not easily affected by temperature changes and can stably maintain sealing performance can be provided. Furthermore, the edge portion 95f of the fifth embodiment can also be applied to the first embodiment, the modified example, the second embodiment, the third embodiment, and the fourth embodiment described above. That is, in a structure in which the width dimension of the blade portion 92 decreases or is the same from the first curved portion 93 side toward the second curved portion 95 side, an abutment portion 97 with 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 sidewall of the guide portion 10 can also be formed.

[0083] Furthermore, the embodiments and variations described above merely illustrate representative aspects of the present invention, and the invention is not limited thereto. For example, a sliding four-way switching valve 100 used in a refrigeration cycle system with the valve device driven by a pilot valve (not shown) has been described, but this is merely an example; the valve device could also be an electric valve equipped with a stepper motor and a threaded feed mechanism. Alternatively, the valve device could be a solenoid valve equipped with an electromagnetic coil and a plunger. Furthermore, the valve device of this embodiment functions as a four-way valve that switches the flow through four flow paths, but the number of flow paths is not limited to this; it can 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. Additionally, the valve device could be a mechanical expansion valve serving as a throttling device, a mechanical pressure regulating valve that drives a pressure-sensing component connected to the valve component according to pressure changes, or a manually operated valve with an operating part that moves the valve core forward and backward. Furthermore, the valve device can be used in systems other than refrigeration cycle systems, and can also be used in structures that control various fluids.

[0084] Symbol Explanation

[0085] L—Axis, 10—Guide section, 14—First working chamber (multiple spaces), 15—High pressure chamber (multiple spaces), 16—Second working chamber (multiple spaces), 40—Valve core, 50—Piston (moving part), 70—Sealing section, 80—L-shield, 81—Base, 82—Rim section, 90—Leaf spring, 91—Base plate section, 92—Blade section, 93—First curved section (curved section), 94—First blade section (plate section), 95—Second curved section (end edge section), 100—Sliding four-way switching valve (valve device, sliding switching valve).

Claims

1. A valve device comprising: a cylindrical guide portion; a movable member that moves along an axis of the guide portion; and a valve core connected to the movable member and controlling the flow of fluid, characterized in that... The moving component is provided with a sealing part that divides the space within the guide portion into multiple spaces. The sealing portion includes: an L-shaped gasket that fits into the inner surface of the guide portion; and a leaf spring that acts on the L-shaped gasket. The L-shaped gasket includes: a plate-shaped base extending intersecting the axis; and a rim portion that rises from the edge of the base and slides in contact with the inner surface of the guide portion. The leaf spring includes: a plate-shaped base portion disposed on the inner surface side of the base portion; and a plurality of leaf portions radially projecting from the base portion about the axis, wherein the rim portion is pressed towards the guide portion by pressing the rim portion from the inner surface side to the outer surface side. The blade portion includes: a curved portion that forms a boundary with the base plate portion; a plate portion that rises from the curved portion; and an end edge portion that is disposed on the front end side of the plate portion and abuts against the rim portion. The width of the plate portion either decreases or remains the same as the width from the curved portion side toward the end edge side.

2. The valve device according to claim 1, characterized in that, The plate has straight sections at both ends in the width direction, which connect the curved section to the end edge.

3. The valve device according to claim 1, characterized in that, The plate portion has two ends in the width direction: a tapered portion that is inclined toward each other as it approaches the end edge; and a straight portion that is continuous with the end edge of the tapered portion and extends toward the end edge and is parallel to each other.

4. The valve device according to claim 1, characterized in that, The plate has curved portions at both ends in the width direction, and these curved portions approach each other as they move toward the end edge.

5. The valve device according to claim 1, characterized in that, An arcuate portion is provided at the edge of the substrate portion to connect the curved portions of the adjacent blade portions to each other. The arc portion is formed in an arc shape that protrudes to the side opposite to the protruding direction of the blade portion. When the radius of the arc portion is set to R and the thickness of the blade portion is set to t, t≤R≤5t.

6. The valve device according to any one of claims 1 to 5, characterized in that, The blade portion has a contact portion that abuts against the wheel rim portion at both ends in the width direction. The abutting portion has a predetermined length from the end edge toward the curved portion, and is inclined or parallel to each other as it approaches the protruding side toward the blade portion.

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

8. The valve device according to claim 7, characterized in that, A second plate portion extending from the end edge toward the inside of the leaf spring is provided in the blade portion. The abutting portion has a predetermined length, extending across the end edge, and is inclined or parallel to each other as it approaches the protruding side of the blade portion.

9. A valve device comprising: a cylindrical guide portion; a movable member that moves along an axis of the guide portion; and a valve core connected to the movable member and controlling the flow of fluid, characterized in that... The moving component is provided with a sealing part that divides the space within the guide portion into multiple spaces. The sealing portion includes: an L-shaped gasket that fits into the inner surface of the guide portion; and a leaf spring that acts on the L-shaped gasket. The L-shaped gasket includes: a plate-shaped base extending intersecting the axis; and a rim portion that rises from the edge of the base and slides in contact with the inner surface of the guide portion. The leaf spring includes: a plate-shaped base portion disposed on the inner surface side of the base portion; and a plurality of leaf portions radially projecting from the base portion about the axis, wherein the rim portion is pressed towards the guide portion by pressing the rim portion from the inner surface side to the outer surface side. The blade portion includes: a curved portion that forms a boundary with the base plate portion; a plate portion that rises from the curved portion; and an end edge portion that is disposed on the front end side of the plate portion and abuts against the rim portion. On the outer surface side of the end edge portion, the two ends in the width direction and the edge portion connecting the two ends in the width direction together constitute an abutment portion that abuts against the rim portion. The curvature of the rim portion is approximately the same as the curvature of the inner surface of the rim portion.

10. A refrigeration circulation system comprising a sliding switching valve, characterized in that, The sliding switching valve is composed of the valve device described in claim 1 or 9.

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