Valve device and refrigeration cycle system

Abstract

The present application aims to provide a valve device and a refrigeration cycle system with improved sealing performance. A check valve (1) includes a cylindrical main body (10) through which fluid flows, a valve seat member (20) pressed into the main body (10), and a valve core (50) that opens and closes a valve port (31) provided in the valve seat member (20). A press-in portion (33) is provided on the outer surface of the valve seat member (20). A press-in portion (13) that is in sliding contact with the press-in portion (33) from the other side (L2) to the one side (L1) is provided on the inner surface of the main body. A protruding surface portion (15) that protrudes toward the inside of the main body (10) is provided at a position of the press-in portion (13) that is closer to the one side (L1) than to the other side (L2), and a sealing portion (S) that prevents leakage of fluid is formed by the close contact of the protruding surface portion (15) with the press-in portion (33) of the valve seat member (20).

Description

Technical Field

[0001] This invention relates to valve devices and refrigeration circulation systems. Background Technology

[0002] Valve devices for controlling fluid flow are known (see, for example, Patent Document 1). The valve device (check valve) described in Patent Document 1 includes a tubular valve core housing, a cylindrical valve seat member housed within the valve core housing, and a valve core (valve body) that opens and closes a valve port formed on the valve seat member. In this valve device, the valve core moves back and forth along the axial direction within the valve core housing to open and close the valve port, thereby controlling fluid flow. Furthermore, the valve seat member is pressed into the valve core housing in the axial direction, thereby sealing the outer wall of the valve seat member against the inner wall of the valve core housing.

[0003] Existing technical documents

[0004] Patent documents

[0005] Patent Document 1: Japanese Patent Application Publication No. 2012-145215 Summary of the Invention

[0006] The problem that the invention aims to solve

[0007] However, the aforementioned valve device is sometimes used, for example, as part of a refrigeration cycle system. In such cases, ultra-high pressure fluids, such as CO2, are sometimes used for the fluid controlled by the valve device. Due to the ultra-high pressure, the force acting in the direction of expanding the inner diameter of the valve core housing is large. Therefore, in a conventional valve device where only the valve core housing is pressed into the valve seat component, the seal between the outer wall of the valve seat component and the inner wall of the valve core housing is insufficient, potentially causing internal leakage where fluid leaks into unexpected areas. Furthermore, this internal leakage can reduce the energy efficiency of the refrigeration cycle system and decrease the energy-saving performance of the valve device.

[0008] The purpose of this invention is to provide a valve device and a refrigeration circulation system with improved 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 comprises a cylindrical body extending from one side to the other and through which fluid flows, a valve seat member pressed into the body, and a valve core for opening and closing a valve port provided on the valve seat member. The valve device is characterized by comprising: a pressing portion provided on the outer surface of the valve seat member; and a pressed-in portion provided on the inner surface of the body, which slides in contact with the pressing portion from the other side to the first side. A protruding surface portion protruding toward the inside of the body is provided at a position of the pressed-in portion closer to the first side than the other side. The tight contact between the pressing portion and the protruding surface portion constitutes a sealing portion that prevents leakage of the fluid.

[0011] According to this invention, a protruding part is provided in the pressed-in portion of the inner surface of the main body, and a sealing part is formed by the tight contact between the pressed-in portion of the valve seat component and the protruding part. This sealing part reliably prevents internal leakage of fluid flowing within the main body to unexpected parts. Therefore, the sealing performance of the valve device can be improved. Thus, even when the fluid controlled by the valve device is, for example, a high-pressure fluid such as CO2, a higher sealing performance can be maintained compared to the conventional valve device structure where only the seat component is pressed into the valve core housing. Therefore, a valve device with improved sealing performance can be provided.

[0012] Furthermore, it is preferable that the protruding surface is formed from an existing surface that was formed before the valve seat component was pressed in. With this structure, the protruding surface is formed from an existing surface that was formed before the valve seat component was pressed in, allowing the pressed portion of the valve seat component to come into close contact with the existing surface pre-formed in the main body to form a seal. Therefore, compared to conventional valve devices that do not have an existing surface that comes into close contact with the pressed portion of the valve seat component, internal leakage of the fluid can be prevented even when using ultra-high pressure fluid as the controlled object of the valve device. Furthermore, the sealing performance of the valve device can be maintained at a higher level.

[0013] Furthermore, the feature is that the protruding surface is formed at a predetermined angle relative to the axis of the main body extending from one side to the other. With this structure, the protruding surface can be formed into various shapes, such as a conical shape inclined relative to the axis of the main body, or a right-angled shape orthogonal to the axis of the main body. Moreover, since the angle of the protruding surface relative to the axis can be set to a predetermined angle, by changing this angle, the tight contact state between the press-in portion and the protruding surface can be appropriately varied according to conditions such as the materials of the main body and the valve seat component. Therefore, the sealing performance of the valve device can be maintained to a higher degree.

[0014] Preferably, the main body and the valve seat component are cylindrical, and the pressed-in portion includes a pressing-in portion on the other side, a small-diameter portion on one side, and a protruding portion between the pressing-in portion and the small-diameter portion. The inner diameter of the pressing-in portion of the valve seat component before pressing in is smaller than the outer diameter of the pressing-in portion in the valve seat component before pressing in. The small-diameter portion has an inner diameter smaller than the inner diameter of the pressing-in portion. The end of the protruding portion on the other side is continuous with the pressing-in portion, and the end of the protruding portion on one side is continuous with the small-diameter portion. With this structure, the valve seat component can be reliably pressed into the main body, and a seal can be reliably formed between the protruding portion and the pressing-in portion.

[0015] Furthermore, preferably, the thickness of the small-diameter portion is larger than the thickness of the press-in portion. In valve devices, for example, a small-diameter portion is sometimes riveted radially inward to fix a valve seat component pressed into the main body. In this case, by forming the riveting portion, a portion of the small-diameter portion may become thinner. In this case, stress under the pressure of ultra-high pressure fluid tends to concentrate at the riveting portion, and the pressure resistance of the main body may locally decrease. However, according to this structure, when the riveting portion is formed, the thickness of the small-diameter portion becomes locally smaller at the riveting portion, but the original thickness of the small-diameter portion is larger than the thickness of the press-in portion, so the pressure resistance of the main body does not locally decrease. Therefore, cracks in the main body are easily prevented, and by preventing cracks, the risk of external fluid leakage can be reduced, and the reliability of the valve device for ultra-high pressure fluids can be improved.

[0016] Furthermore, preferably, the outer diameter of the smaller diameter portion is equal to the outer diameter of the pressing portion. With this structure, since the outer diameter of the smaller diameter portion is equal to the outer diameter of the pressing portion, steps or other defects caused by the difference in outer diameter will not form in the main body. Therefore, it is difficult to form stress concentration areas such as boundary portions with steps in the main body. Consequently, stress corrosion cracks caused by stress concentration can be easily prevented, and the reliability of valve devices for ultra-high pressure fluids can be improved.

[0017] Furthermore, the check valve of the present invention is characterized by being constructed from the valve device described in any of the above-mentioned claims. According to this invention, a check valve can be constructed using a valve device that improves sealing performance.

[0018] Furthermore, the refrigeration cycle system of the present invention is characterized by including the check valve described above. According to this invention, since a check valve with improved sealing performance can be used to construct the refrigeration cycle system, the energy efficiency of the refrigeration cycle system is improved.

[0019] Furthermore, preferably, a large-diameter portion with an inner diameter larger than that of the press-in portion is provided on the other side of the aforementioned press-in portion. The valve seat component has a flange portion that protrudes toward the inner surface of the main body and abuts against the boundary between the large-diameter portion and the press-in portion on the inner surface. The space enclosed by the flange portion and the portion other than the flange portion in the valve seat component, and the press-in portion in the main body, constitutes an oil reservoir capable of accumulating oil contained in the fluid. An oil inlet portion is provided on the flange portion to communicate with the interior of the main body. The oil reservoir and the oil inlet portion constitute a working fluid leakage prevention part that suppresses fluid leakage. With this structure, oil accumulated in the oil reservoir can be supplied to the space between the outer surface of the valve seat component and the inner surface of the main body through capillary action. Therefore, for example, assuming there are small gaps or scratches between the press-in portion on the outer surface of the valve seat component and the press-in portion on the inner surface of the main body, the oil can be used to more reliably suppress internal fluid leakage. Furthermore, the oil accumulated in the oil reservoir is difficult to move to the other side because the flange abuts against the main body. Therefore, compared to a structure where the oil reservoir is formed by only providing a gap between the valve seat component and the main body, the following situation can be suppressed: that is, the so-called jetting effect of oil being drawn out of the oil reservoir due to the flow of fluid around the oil reservoir can be prevented.

[0020] Furthermore, preferably, the main body has a retaining force reinforcing portion that strengthens the retaining force of the pressed-in portion. This retaining force reinforcing portion is formed by the pressed-in portion, which has undergone plastic processing, and the thickness of the pressed-in portion is smaller than the thickness of the small-diameter portion. With this structure, for example, by performing plastic processing such as spinning on the pressed-in portion, the hardness of the pressed-in portion can be made higher than that of the small-diameter portion, making the pressed-in portion less prone to deformation. Therefore, even if the internal structure of the main body undergoes repeated changes such as expansion or contraction due to changes in pressure and temperature, the retaining strength of the valve seat component for the pressed-in portion can be maintained at a high level, ensuring stable sealing of the sealing portion and improving the anti-disengagement strength of the valve seat component.

[0021] Furthermore, preferably, the valve seat component has a corner portion with a surface facing the other end of the valve seat component on its outer periphery, and the main body has a riveting portion that rivets inward, and the riveting portion has a riveting protrusion that engages with the corner portion. With this structure, the riveting protrusion of the riveting portion in the main body engages with the corner portion of the valve seat component, suppressing riveting loosening and further improving the holding force of the valve seat component in the main body, thus further improving the anti-detachment strength of the valve seat component.

[0022] Furthermore, preferably, the aforementioned riveting protrusion is composed of the front end of the riveting portion formed on the outer periphery of the main body by stamping and riveting and protruding inward toward the main body. With this structure, compared to a so-called roll riveting structure where riveting is performed throughout the entire circumference of the main body, the stress generated at the riveting portion can be reduced. Therefore, cracks in the main body and external leakage of fluid caused by cracks can be suppressed.

[0023] Furthermore, preferably, the aforementioned riveting protrusion engages with at least a portion of the aforementioned corner portion, and this engaged portion constitutes a working fluid leakage prevention part that suppresses the leakage of the aforementioned fluid. According to this structure, by embedding the riveting protrusion of the main body into at least a portion of the corner portion of the valve seat component, riveting loosening of the riveting portion can be further suppressed, and the pressed-in valve seat component is less likely to loosen relative to the main body. Therefore, the holding force of the main body on the valve seat component can be further improved, thereby further improving the anti-loosening strength of the valve seat component. Furthermore, at this time, the valve seat component and the main body are closer in the engaging direction. As a result, the pressed-in portion constituting the sealing portion contacts the protruding surface more tightly, increasing the surface pressure of the sealing portion. Therefore, the sealing performance of the sealing portion is further improved. Therefore, the working fluid leakage prevention part that suppresses fluid leakage, formed by this engaged portion, can suppress internal leakage of the fluid.

[0024] Furthermore, preferably, an inwardly recessed annular recess is provided on one side of the valve seat component, and the end of the one side of the annular recess forms the corner portion. In the axial direction of the main body, the dimension of the valve seat component from the end of one side to the corner portion is at least 0.5 times the dimension from the corner portion to the end of the other side of the riveting protrusion. With this structure, the axial dimension from the portion forming the corner portion to the end of one side of the valve seat component can be ensured, thus ensuring the strength of one side of the valve seat component. Therefore, deformation of one side of the valve seat component can be suppressed, and thus, when the riveting protrusion engages with the corner portion, the anti-detachment strength of the valve seat component can be further improved.

[0025] The effects of the invention are as follows.

[0026] According to the present invention, a valve device and a refrigeration circulation system with improved sealing performance can be provided. Attached Figure Description

[0027] Figure 1 This is a cross-sectional view of a check valve according to one embodiment of the present invention, cut along the axial direction.

[0028] Figure 2 (A) is a sectional view of the main body of the valve seat component before it is pressed in, cut along the axial direction; (B) is an enlarged sectional view of the valve seat component before it is pressed in, cut along the axial direction.

[0029] Figure 3(A) is an enlarged view of the main part of the check valve body before the valve seat assembly is pressed in, and (B) is a view of the valve seat assembly after it is pressed in. Figure 1 This is an enlarged view of region A, and it is a diagram showing the dimensional relationships of the various parts surrounding the pressed-in portion.

[0030] Figure 4 (A) is a cross-sectional view of the main body of the check valve with the pressed-in part cut along the axial direction; (B) is a cross-sectional view of the main body with the inlet pipe cut along the axial direction; and (C) is a cross-sectional view of the main body after the valve seat component is pressed in, cut along the axial direction.

[0031] Figure 5 (A) to (C) are simplified diagrams showing the changes in the existing face and the press-in portion of the valve seat component of the main body.

[0032] Figure 6 (D) to (F) show the existing face and the press-in portion of the valve seat component of the main body, excluding... Figure 5 A simplified diagram of the changes other than those shown in (A) to (C).

[0033] Figure 7 (A) is a sectional view of the main body and valve seat assembly just before they are pressed in, cut along the axial direction; (B) is a sectional view cut along the axial direction. Figure 7 (A) shows a cross-sectional view of the main body and valve seat component when the valve seat component is pressed in.

[0034] Figure 8 (A) is shown Figure 7 (A) is a simplified diagram showing the dimensional relationships of the parts of the press-in portion before the valve seat assembly is pressed in, and (B) is a diagram showing the valve seat assembly after it has been pressed in relative to the press-in portion. Figure 7 A simplified diagram showing the dimensional relationships of the various parts of the pressed-in section, as shown in (B).

[0035] Figure 9 (A) and (B) are simplified diagrams showing the changes in the dimensional relationships of the various parts of the pressed-in portion before the valve seat component is pressed in.

[0036] Figure 10 This is a schematic diagram of a refrigeration circulation system equipped with a check valve.

[0037] Figure 11 This is a cross-sectional view of the check valve of the second embodiment, cut along the axial direction.

[0038] Figure 12 This is a cross-sectional view of the valve seat component of the second embodiment, cut along the axial direction.

[0039] Figure 13 yes Figure 11 The diagram shows an enlarged view of the main parts of the check valve.

[0040] Figure 14 This is a cross-sectional view of the check valve of the third embodiment, cut along the axial direction.

[0041] Figure 15 (A) is a cross-sectional view of the valve seat component of the third embodiment, cut along the axial direction; (B) is... Figure 14 An enlarged sectional view of region I in the diagram.

[0042] Figure 16 (A) to (D) are side views of the main body used to show the changes in the riveting.

[0043] Figure 17 (A) is Figure 14 An enlarged view of region II in the image, (B) is... Figure 15 (A) is a sectional view along line AA, and (C) is a sectional view showing another embodiment of the oil inlet.

[0044] Figure 18 This is a cross-sectional view of the check valve of the fourth embodiment, cut along the axial direction.

[0045] Figure 19 yes Figure 18 A magnified view of region III. Detailed Implementation

[0046] The following is based on Figures 1-10 The check valve 1 according to the first embodiment of the present invention will be described. The check valve 1 of this embodiment is a valve device for controlling (allowing flow, preventing flow) of fluid, and is used, for example, in the middle of the fluid flow path in the refrigeration circulation system 100 described below. Furthermore, in the following description, the direction along the axis L of the main body 10 described below will be referred to as "axis L direction," one side of the axis L direction will be referred to as "one side L1," and the other side of the axis L direction will be referred to as "the other side L2." Furthermore, the direction from one side L1 to the other side L2 will be considered the forward flow direction of the fluid, and the direction opposite to the forward flow direction will be considered the reverse flow direction. This is merely for ease of explanation and does not necessarily correspond to the actual operating direction of the check valve 1; the directions of the check valve 1 in its actual operating state are not limited.

[0047] like Figure 1As shown, the check valve 1 includes a body 10 extending from one side L1 to the other side L2. Although fluid flows in the body 10 in either the forward or reverse direction, the flow in the reverse direction is prevented by the valve core 50 described below. The body 10 includes a valve body 11 formed in a cylindrical shape using a metal material such as copper and extending along the axis L. A large-diameter portion 12 is formed on the other side L2 of the inner circumferential surface (inner surface) of the valve body 11. The large-diameter portion 12 is the part with the largest inner diameter in the valve body 11 and is cylindrical. A pressed-in portion 13 with an inner diameter smaller than that of the large-diameter portion 12 is continuously formed on one side L1 of the large-diameter portion 12 and extends toward one side L1. The pressed-in portion 33 of the valve seat member 20, which is pressed into the valve body 11, slides in contact with the pressed-in portion 13 from the other side L2 toward one side L1 (pressed into the pressed-in portion 13).

[0048] like Figure 2 (A) Figure 3 As shown in (A), the pressed-in portion 13, extending from one side L2 toward the other side L1, includes a pressing-in amount portion 14, a protruding portion 15, and a small-diameter portion 16. Furthermore, the "pressing-in amount" of the "pressing-in amount portion 14" generally refers to the radial difference between the outer diameter β1 of the pressing-in portion 33 of the valve seat component 20 and the inner diameter of the pressed-in portion 13 of the valve body 11; "pressing-in amount portion 14" indicates the range of this "pressing-in amount" in the axial direction L within the valve body 11. The pressing-in amount portion 14 is continuous with the large-diameter portion 12 and is formed in a cylindrical shape. Figure 2 In the press-in portion 14 shown in (A), the inner diameter α1 of the valve seat component 20 before press-in is set to be smaller than the inner diameter of the large diameter portion 12, and smaller than... Figure 2 The outer diameter β1 of the press-in portion 33 in the valve seat component 20 before press-in, as shown in (B), is small. Utilizing the difference between this inner diameter α1 and the outer diameter β1 (press-in amount), the valve seat component 20 is reliably pressed into the valve body 11. Figure 3 As shown in (A), the protruding part 15 is an inner wall surface that protrudes radially inward (inward of the main body 10), with the end of the other side L2 continuous with the pressing part 14, and the end of the other side L1 continuous with the small diameter part 16. That is, the protruding part 15 is located between the pressing part 14 and the small diameter part 16 at a position on the side L1 closer to the end of the other side L2 in the pressed part 13, and protrudes inward toward the main body 10.

[0049] The protruding face 15 is formed at a predetermined angle θ1 relative to the axis L. Furthermore, the predetermined angle θ1 is... Figure 2 The angle formed by the portion where the wall surface of the upper protruding face 15 and the lower protruding face 15 intersect when they extend to one side L1 in the cross-sectional view shown in (A) can be appropriately set. Figure 3As shown in (A), the protruding face 15 has a pre-formed face 15a that is formed before the valve seat component 20 is pressed in. That is, the protruding face 15 is composed of the pre-formed face 15a. Furthermore, the details of the formation of the protruding face 15 are described below.

[0050] The small-diameter portion 16 is the inner wall surface that constitutes one side L1 of the pressed-in portion 13, and is formed into a cylindrical shape that extends continuously to one side L1 from the protruding portion 15. Figure 3 As shown in (A), the inner diameter α2 of the small diameter portion 16 is set to be less than or equal to the inner diameter α1 of the press-in portion 14. Figure 1 As shown, in the valve body 11, a riveting portion 17 is formed on one side L1 of the pressed-in portion 13, which engages with the pressed-in valve seat component 20. The riveting portion 17 is formed by riveting one side L1 of the valve body 11 from the radially outward to the radially inward, and engages with at least one side L1 end of the annular recess 34 of the valve seat component 20 described below. The inlet pipe 18 is continuous with the end of one side L1 of the valve body 11 formed in this way.

[0051] The inlet pipe 18 extends towards one side L1 and is formed in a cylindrical shape. The inlet pipe 18 has a large-diameter inlet pipe 18a continuous with one side L1 of the valve body 11 and a small-diameter inlet pipe 18b continuous with one side L1 of the large-diameter inlet pipe 18a. The outer diameter of the small-diameter inlet pipe 18b is smaller than the outer diameter of the large-diameter inlet pipe 18a. On the other hand, the outlet pipe 19 is continuous with the end of the valve body 11 on the other side L2. The outlet pipe 19 has a small-diameter outlet pipe 19a continuous with the valve body 11 and a large-diameter outlet pipe 19b continuous with the other side L2 of the small-diameter outlet pipe 19a. The outer and inner diameters of the large-diameter outlet pipe 19b are larger than the outer and inner diameters of the small-diameter outlet pipe 19a. Within the valve body 11 of the body 10, the valve seat component 20 is pressed in from the other side L2 toward one side L1 and is thus housed.

[0052] The valve seat component 20 is made of a metal such as brass and is formed into a cylindrical shape. For example... Figure 2 As shown in (B), the valve seat component 20 has a cylindrical valve seat portion 30 extending along the axis L. A valve port 31 extending along the axis L is formed at the center of the valve seat portion 30. The opening end of the valve port 31 on the other side L2 expands radially outward to form a stepped shape, and this stepped portion constitutes a valve seat 32. A press-in portion 33 is formed on the outer peripheral surface (outer surface) of the valve seat portion 30, which slides in contact with the press-in portion 13 of the main body 10 (pressed into the press-in portion 13 of the main body 10). The press-in portion 33 has a flat portion 33a extending along the axis L and an inclined portion 33b that is continuous with the flat portion 33a and inclined relative to the axis L. The flat portion 33a extends substantially parallel to the axis L. The inclined portion 33b (press-in portion 33) is formed to have a predetermined angle θ2 relative to the axis L.

[0053] Furthermore, the predetermined angle θ2 is in Figure 2 The angle formed by the portions where the upper inclined surface 33b and the lower inclined surface 33b intersect when they extend to one side L1, as shown in the cross-sectional view (B), can be appropriately set. The inclined surface 33b is in close contact with the protruding surface 15 when the valve seat component 20 is pressed into the valve body 11. Furthermore, as... Figure 1 As shown, a sealing portion S is formed by the tight contact portion where the inclined surface 33b and the protruding surface 15 are in close contact. By forming the sealing portion S, internal leakage of fluid into unexpected parts is prevented. Specifically, when the fluid flows in the countercurrent direction, leakage is prevented from the press-in portion 33 of the valve seat component 20 and the press-in portion 13 of the valve body 11, except for the seat portion where the valve core 50 contacts the valve seat 32. An annular recess 34 is formed on one side L1 of the press-in portion 33, which is radially inward. The riveting portion 17 of the valve body 11 engages with the annular recess 34. This restricts the displacement of the valve seat component 20 pressed into the valve body 11 along the axis L, preventing the valve seat component 20 from dislodging from the valve body 11. On the other hand, a flange portion 35 is formed on the other side L2 of the press-in portion 33, which protrudes radially outward. The flange portion 35 is formed around the entire circumference of the axis L.

[0054] The flange portion 35 is configured to abut against the boundary between the large-diameter portion 12 and the pressed-in portion 13 of the main body 10 on one side L1. When the flange portion 35 abuts against the boundary between the large-diameter portion 12 and the pressed-in portion 13, it restricts the displacement of the valve seat component 20 to one side L1. A valve holder portion 40 is formed on the other side L2 of the valve seat portion 30. The valve holder portion 40 is formed as a cylindrical shape that extends vertically from the end of the valve seat portion 30 on the other side L2. The interior of the valve holder portion 40 forms a valve chamber 41, in which the valve core 50 is housed. The outer diameter of the valve holder portion 40 is set to be smaller than the inner diameter of the valve body 11. Four radially penetrating through-holes 42 are formed on the peripheral wall surface of the valve holder portion 40. Thus, the valve chamber 41 communicates with the interior of the valve body 11. A valve limiting member 43 is mounted on the inner surface of the end of the valve holder portion 40 on the other side L2. The valve limiting member 43 is formed in a roughly circular shape using a metal material such as stainless steel, and functions as a retaining ring to limit the movement of the valve core 50 to the other side L2 after it comes into contact with the valve.

[0055] The valve core 50, housed in the valve holder section 40, is formed of resin material and is cylindrical. The valve core 50 is designed to slide within the valve chamber 41 along the axis L, opening and closing the valve port 31 by moving forward and backward along the axis L. Figure 2As shown in (B), the valve core 50 has a generally cylindrical valve core body 51. Four grooves 52 extending along the axis L are formed on the outer surface of the valve core body 51, so that the cross-sectional shape of the valve core body 51 intersecting the axis L is approximately cross-shaped. By forming the grooves 52, only the approximately cross-shaped outer periphery slides relative to the inner periphery of the valve holder 40, so the movement resistance of the valve core 50 relative to the valve holder 40 about the axis L is reduced, and the sliding movement of the valve core 50 is smooth. A thinning portion 53 is formed in the center of the valve core body 51, which thins from the center of the end face of the other side L2 toward one side L1 in a non-through manner. The thinning portion 53 suppresses shrinkage, bubbles, etc. during the resin molding of the valve core 50, and contributes to the weight reduction of the valve core 50. The end face of one side L1 of the valve core body 51 forms a sealing surface 54 that closes the valve port 31 by abutting against the valve seat 32.

[0056] Next, the manufacturing of check valve 1 will be described. First, a cylinder 10a extending along the axis L is formed using a metal material such as copper. Then, as... Figure 4 As shown in (A), the pressing portion 14, the protruding portion 15, and the small diameter portion 16 are formed relative to the cylinder 10a as the pressing portion 13.

[0057] In the pressed-in part 13, such as Figure 3 As shown in (A), the inner diameter α2 of the small diameter portion 16 is less than or equal to the inner diameter α1 of the pressed-in portion 13. Furthermore, as... Figure 3 As shown in (A), before the valve seat component 20 is pressed in, the thickness T1 (wall thickness) of the small-diameter portion 16 is larger than the thickness T2 (wall thickness) of the pressing portion 14. Furthermore, the outer diameter D1 of the small-diameter portion 16 is equal to the outer diameter D2 of the pressing portion 14. In this embodiment, the protruding portion 15 of the pressed portion 13 formed in this stage is specifically designated as a pre-existing portion 15a. The pre-existing portion 15a can be formed with various shapes and tilt angles. Figure 5 (A) to (C) are simplified diagrams showing the changes in the existing face 15a (protruding face 15) of the main body 10 and the press-in portion 33 of the valve seat component 20. Figure 6 (D) to (F) show the existing face 15a of the main body 10 and the press-in portion 33 of the valve seat component 20, excluding... Figure 5 A simplified diagram of the changes other than those shown in (A) to (C). For example... Figure 5 As shown in (A), the face 15a can be formed such that its predetermined angle θ1 is equal to the predetermined angle θ2 of the inclined face 33b (press-in portion 33).

[0058] And, as Figure 5 As shown in (B), face 15a can be formed such that its predetermined angle θ1 is larger than the predetermined angle θ2 of the tilted face 33b. Furthermore, as... Figure 5 As shown in (C), face 15a can be formed such that its predetermined angle θ1 is smaller than the predetermined angle θ2 of the tilted face 33b. Furthermore, as... Figure 6 As shown in (D), the face 15a can be formed such that the predetermined angle θ1 becomes 90°. Furthermore, as... Figure 6 As shown in (E), the existing face 15a can also be formed such that the end (edge ​​portion) of the other side L2 and the end (edge ​​portion) of one side L1 have curved R portions (arc portions) 14c. Furthermore, as... Figure 6 As shown in (F), the existing face 15a can also be formed radially inward in such a way that the predetermined angle θ1 is 90°.

[0059] Next, as Figure 4 As shown in (B), one side L1 portion of the cylinder 10a is machined to form an inlet pipe 18 having a large-diameter inlet pipe 18a and a small-diameter inlet pipe 18b. Then, as... Figure 4 As shown in (C), the valve seat component 20 is pressed into one side L1 from the end of L2 on the other side of the cylinder 10a. At this time, the sealing part S is formed as follows. Specifically, if as Figure 7 As shown in (A), starting from the position where the inclined portion 33b of the valve seat 30 is located on the other side L2 relative to the press-in portion 14, the valve seat 30 is pressed (pressed in) relative to the cylinder 10a from the other side L2 to one side L1, then as Figure 7 As shown in (B), the valve seat 30 moves to one side L1 and is pressed in. Then, as... Figure 7 As shown in (B), the inclined surface 33b of the press-in portion 33 is in close contact with the existing surface 15a (protruding surface 15), and the close contact portion constitutes the sealing portion S. In this way, the press-in portion 33 of the valve seat component 20 is pressed into the press-in amount portion 14, and the inclined surface 33b constitutes the sealing portion S.

[0060] Furthermore, in the case where the protruding face 15 (face 15a) is pre-formed as in this embodiment, the dimensional relationship between the various parts of the pressed-in portion 13 before and after the valve seat component 20 is pressed in is as follows: Figure 8 The relationship shown in (A) and (B). Figure 8 (A) is shown Figure 7 (A) is a simplified diagram showing the dimensional relationships of the various parts of the inner circumferential surface of the main body 10 before the valve seat component 20 is pressed in. Figure 8 (B) shows the valve seat component 20 after being pressed into the valve seat relative to the pressed-in portion 13. Figure 7 A simplified diagram showing the dimensional relationships of the various parts of the pressed-in portion 13, as shown in (B). Figure 8As shown in (A), before the valve seat component 20 is pressed in, the relationship between the inner diameter α1 of the pressing portion 14, the inner diameter α2 of one side portion 16a of the small diameter portion 16, and the inner diameter α4 of the other side portion 16b of the small diameter portion 16 is that inner diameter α1 > inner diameter α2 = inner diameter α4. On the other hand, as Figure 8 As shown in (B), after the valve seat component 20 is pressed in, the relationship between the inner diameter α6 of the pressing portion 14, the inner diameter α2 of one side portion 16a of the small diameter portion 16, and the inner diameter α4 of the other side portion 16b of the small diameter portion 16 is that the inner diameter α6 > the inner diameter α2 = the inner diameter α4.

[0061] That is, the size relationship of the inner diameters of the pressing portion 14, one side portion 16a of the small diameter portion 16, and the other side portion 16b of the small diameter portion 16 remains unchanged before and after the valve seat component 20 is pressed in. This relationship of the inner diameters of the pressing portion 14, one side portion 16a of the small diameter portion 16, and the other side portion 16b of the small diameter portion 16 before the valve seat component 20 is configured to be consistent with... Figure 8 The relationship shown in (A) remains the same regardless of the specific circumstances. Figure 9 (A) and (B) are simplified diagrams showing the changes in the dimensional relationships of the various parts of the pressed-in portion 13 before the valve seat component 20 is pressed in. Figure 9 As shown in (A), before the valve seat component 20 is pressed in, the relationship between the inner diameter α1 of the pressing portion 14, the inner diameter α2 of one side portion 16a of the small diameter portion 16, and the inner diameter α4 of the other side portion 16b of the small diameter portion 16 is that the inner diameter α2 < the inner diameter α1 = the inner diameter α4.

[0062] And, as Figure 9 As shown in (B), before the valve seat component 20 is pressed in, the relationship between the inner diameter α1 of the pressing portion 14, the inner diameter α2 of one side portion 16a of the small diameter portion 16, and the inner diameter α4 of the other side portion 16b of the small diameter portion 16 is that inner diameter α4 < inner diameter α2 < inner diameter α1. Thus, the dimensional relationships of each part are... Figure 8 In the different structures of the above embodiments shown in (A) and (B), although the valve seat component 20 is not shown after being pressed in, the size relationship of the inner diameters of the pressing portion 14, one side portion 16a of the small diameter portion 16, and the other side portion 16b of the small diameter portion 16 does not change before and after the valve seat component 20 is pressed in.

[0063] Furthermore, the valve seat component 20, which is pressed into the valve body 11, is restricted from moving to one side L1 by abutting against the boundary between the large-diameter portion 12 and the pressed-in portion 13 of the valve body 11 via the flange portion 35. This abutment completes the pressing of the valve seat component 20. After the valve seat component 20 is pressed in, as... Figure 4As shown in (C), a riveting portion 17 is formed in the valve body 11, and the valve seat component 20 is fixed to the valve body 11 by the engagement of the riveting portion 17 with the annular recess 34. Then, the other side L2 portion of the cylinder 10a is machined, as shown in (C). Figure 1 As shown, an outlet pipe 19 is formed, comprising a small-diameter outlet pipe 19a and a large-diameter outlet pipe 19b. Thus, the manufacturing of the check valve 1 is completed.

[0064] Next, the dimensional relationships around the pressed-in part 13 will be explained in detail. Figure 3 (B) shows the dimensional relationship around the pressed-in portion 13 after the valve seat component 20 is pressed in. Figure 3 In (B), the symbol X indicates the length of the protruding portion 15 of the valve seat component 20 after it is pressed in along the axis L. The symbol Y indicates the length of the protruding portion 15 of the valve seat component 20 after it is pressed in along the radial direction orthogonal to the axis L. The symbol α5 indicates the length of the press-in portion 14 of the valve seat component 20 after it is pressed in along the axis L. Furthermore, in the following description, sometimes the symbol X is only referred to as the length dimension X, the symbol Y as only the height dimension Y, and the symbol α5 as only the length dimension α5. Here, the height dimension Y of the protruding portion 15 is preferably set to be smaller than the thickness dimension T2 (wall thickness) of the press-in portion 14 of the valve seat component 20 after it is pressed in. Specifically, the height dimension Y of the protruding face 15 is preferably set to about 1 / 10 to 1 / 1 times the thickness dimension T2 of the pressing amount portion 14 after the valve seat component 20 is pressed in, more preferably to about 1 / 10 to 1 / 3 times the thickness dimension T2, and even more preferably to be smaller than about 1 / 10 to 1 / 4 times the thickness dimension T2.

[0065] Here, by setting the height dimension Y of the protruding part 15 to a small value, approximately 1 / 10 to 1 / 1 of the thickness dimension T2 of the press-in portion 14 after the valve seat component 20 is pressed in, or setting it to 1 / 10 to 1 / 3 or 1 / 10 to 1 / 4 of the aforementioned thickness dimension T2, the following effects are achieved. For example, when the height dimension Y of the protruding part 15 is set to a large value, such as more than twice (200%) the thickness dimension T2 of the press-in portion 14 after the valve seat component 20 is pressed in, the protruding part 15 functions as a positioning and limiting element for the valve seat component 20 during pressing, but it is not suitable for sealing internal leakage of fluid. This is because the area of ​​the inclined surface of the protruding part 15 is large, and the contact area between the protruding part 15 and the press-in portion 33 is large, thus dispersing the load generated in the close contact between the protruding part 15 and the press-in portion 33. However, in this invention, the height dimension Y of the protruding part 15 is relatively small, approximately 1 / 10 to 1 / 1 time (10 to 100%) of the thickness dimension T2 of the press-in portion 14 after the valve seat component 20 is pressed in. Because the protruding part 15 is so small, the contact area between the press-in portion 33 of the valve seat component 20 and the protruding part 15 is reduced. Therefore, as described above, the close contact load is not dispersed, and the press-fit sealing effect between the protruding part 15 and the press-in portion 33 is improved, thus enhancing the sealing performance. Furthermore, when the height dimension Y is set to approximately 1 / 10 to 1 / 3 time (10 to 33%) of the aforementioned thickness dimension T2, the contact area between the protruding part 15 and the press-in portion 33 is further reduced, thus further enhancing the press-fit sealing effect and improving the sealing performance. Furthermore, when the height dimension Y is set to approximately 1 / 10 to 1 / 4 (10 to 25%) of the aforementioned thickness dimension T2, the close contact area between the protruding face 15 and the press-in portion 33 is further reduced, thus further improving the press-sealing effect and sealing performance.

[0066] Furthermore, the height dimension Y of the protruding face 15 is preferably set to about 4% to 10% of the length dimension α5 of the pressing portion 14, more preferably about 5%. The length dimension X of the protruding face 15 is preferably set to about 20% to 50% of the length dimension α5 of the pressing portion 14. By configuring it in this way, the protruding face 15 can be provided with sufficient length dimension X and height dimension Y relative to the length dimension α5 of the pressing portion 14. Therefore, when a sealing portion S is formed on the protruding face 15, even though the aforementioned close contact area is small, the sealing area can be sufficiently ensured, thereby significantly improving the sealing performance.

[0067] Check valves 1 constructed in this way are used in various configurations. For example, in... Figure 1 When the axis L shown is in the vertical direction, that is, when used in a longitudinally placed position, the operation is as follows. First, when the valve core 50 sits on the valve seat 32 due to its own weight, it is located... Figure 1 When the valve is in the position shown (hereinafter also referred to as the closed position), the fluid flows from the inlet pipe 18 toward the outlet pipe 19 in the forward flow direction. As a result, the valve core 50, pushed by the fluid flowing from the valve port 31, dismounts from the valve seat 32, opening the valve port 31 and moving to the open valve state, abutting against the valve limit member 43. Then, when the fluid flow in the forward direction stops, the valve core 50 falls back onto the valve seat 32 due to its own weight, closing the valve port 31 and becoming the closed valve state. Furthermore, when the check valve 1 is used in a horizontal or vertically inverted position, it operates as follows: First, with the valve core 50 in the closed position, the pressure on the outlet pipe 19 side is set higher than that on the inlet pipe 18 side, causing the fluid to flow in the reverse direction due to this pressure difference.

[0068] Thus, the valve core 50 is pressed against the valve seat 32 and remains seated. In this state, when the pressure in the inlet pipe 18 increases and fluid flows from the inlet pipe 18 side to the outlet pipe 19 side in the forward flow direction, the valve core 50, pressed by the fluid flowing from the valve port 31, dislodles from the valve seat 32. Then, when the fluid flow in the forward flow direction stops, and the pressure on the outlet pipe 19 side is again higher than that on the inlet pipe 18 side, the fluid flows in the reverse flow direction due to this pressure difference. Thus, the valve core 50 re-seated on the valve seat 32. When the fluid flows in this way, in this embodiment, by providing the sealing portion S, internal leakage is prevented from the body 10 and the valve seat component 20 to unexpected parts. Specifically, for example, as described above, when the fluid flows in the reverse flow direction, leakage is prevented from the pressing portion 33 of the valve seat component 20 and the pressed-in portion 13 of the body 10, except for the seated portion where the valve core 50 abuts against the valve seat 32. Furthermore, when the valve core 50 is seated on the valve seat 32, the valve core 50 is pressed against the valve seat 32, and a compressive load is applied to the valve seat component 20 in the valve closing direction. As a result, the inclined surface 33b constituting the sealing part S is pressed against the protruding surface 15, and the inclined surface 33b and the protruding surface 15 are more closely attached, thereby further improving the sealing performance.

[0069] Here, below, use Figure 3 Section (B) explains the dimensional relationships of the valve body 11 after the valve seat component 20 is pressed in. For example... Figure 3 As shown in (B), the thickness T1 of the small-diameter portion 16 is larger than the thickness T2 of the pressing portion 14 (i.e., thickness T1 > thickness T2). Furthermore, the outer diameter D1 of the small-diameter portion 16 is equal to the outer diameter D2 of the pressing portion 14 (i.e., outer diameter D1 = outer diameter D2). Alternatively, the outer diameter D2 can be slightly larger than the outer diameter D1, thereby creating a slight incline (conical shape) that smoothly connects the outer peripheral surface of the small-diameter portion 16 to the outer peripheral surface of the pressing portion 14 without any steps.

[0070] Here, in the check valve described in Patent Document 1 above, such as Patent Document 1... Figure 2 As shown in (b), the thickness of the portion corresponding to the small diameter portion 16 in this embodiment is the same as the thickness of the portion corresponding to the pressing portion 14. When the valve seat component is pressed in, the wall thickness of the valve body receiving portion does not change, but the overall diameter expands. Therefore, the dimension corresponding to the outer diameter dimension D2 in this embodiment (the outer diameter dimension corresponding to the pressing portion 14 in this embodiment) is larger than the dimension corresponding to the outer diameter dimension D1 in this embodiment (the outer diameter dimension corresponding to the small diameter portion 16 in this embodiment), which is different from this embodiment. Furthermore, in the check valve described in Patent Document 1, a stepped portion is formed on the outer peripheral surface of the valve body receiving portion before the valve seat component is pressed in, which is different from this embodiment.

[0071] The reason why the relationship between the thickness of the portion corresponding to the small diameter portion 16 and the portion corresponding to the pressing amount portion 14, as well as the relationship between their outer diameters, differ from that of this embodiment is as follows: The check valve described in Patent Document 1 controls a general fluid in a refrigeration cycle system, not a high-pressure fluid as described in this embodiment. That is, the pressure resistance required for the check valve described in Patent Document 1 is lower than that of this embodiment. Therefore, the wall thickness of the valve body housing portion of the check valve described in Patent Document 1 is, for example, about half that of the valve body 11 in this embodiment, which is quite thin, making the valve body housing portion prone to deformation due to the pressing of the valve seat component. Therefore, as described above, by keeping the thickness of the portion corresponding to the small diameter portion 16 and the thickness of the portion corresponding to the pressing amount portion 14 equal and unchanged, the outer diameter D2 is larger than the outer diameter D1.

[0072] In this embodiment, the thickness T1 of the small-diameter portion 16 is larger than the thickness T2 of the press-in portion 14 (thickness T1 > thickness T2), which yields the following effect. Because the thickness T1 of the small-diameter portion 16 is locally reduced due to the formation of the riveting portion 17, the pressure resistance of the valve body 11 may sometimes decrease locally at the riveting portion 17 when the thickness T1 = thickness T2. However, in this embodiment, the original thickness T1 of the small-diameter portion 16 is larger than the thickness T2 of the press-in portion 14, so even with the formation of the riveting portion 17, the pressure resistance of the valve body 11 will not decrease locally. Therefore, compared to the structure described in Patent Document 1 above, where the thickness of the portion corresponding to the small-diameter portion 16 is the same as the thickness of the portion corresponding to the press-in portion 14, it is easier to prevent cracks in the valve body 11 caused by reduced pressure resistance. Moreover, by preventing this crack, the risk of external fluid leakage can be reduced, and the reliability of check valve 1 for ultra-high pressure fluids can be improved.

[0073] Furthermore, in this embodiment, the outer diameter D1 of the small diameter portion 16 is equal to the outer diameter D2 of the pressing portion 14, which achieves the following effect. Since the outer diameter D1 of the small diameter portion 16 is equal to the outer diameter D2 of the pressing portion 14, stress concentration areas such as steps caused by the difference between the outer diameter D1 and the outer diameter D2 are not formed on the valve body 11, making it difficult to form step boundaries. Therefore, stress corrosion cracking caused by stress concentration is easily prevented. This effect is particularly significant compared to the check valve described in Patent Document 1, where a step is formed on the outer circumferential surface of the valve body housing portion because the size corresponding to the outer diameter D2 is larger than the size corresponding to the outer diameter D1. In other words, in this embodiment, compared to the check valve described in Patent Document 1, stress corrosion cracking of the valve body 11 can be easily prevented, improving the reliability of the check valve 1 for ultra-high pressure fluids.

[0074] Furthermore, as described above, in this embodiment, the aforementioned effect remains the same even when the outer diameter D2 is slightly larger than the outer diameter D1 and has a slight inclination (conical shape) where the outer peripheral surface of the small diameter portion 16 is smoothly connected to the outer peripheral surface of the press-in portion 14 without any steps. This is because, according to this structure, even if there is a difference between the outer diameter D1 and the outer diameter D2, stress concentration portions such as stepped boundary portions will not be formed, thus preventing stress corrosion cracks in the valve body 11.

[0075] Furthermore, in this embodiment, as described above, the thickness dimension T1 > the thickness dimension T2, and the outer diameter dimension D1 = the outer diameter dimension D2. According to this structure, since the thickness dimension T1 > the thickness dimension T2, a protruding portion 15 is formed on the valve body 11. Therefore, the sealing portion S can be formed by the protruding portion 15 and the pressing portion 33, preventing internal leakage of fluid. Furthermore, since the outer diameter dimension D1 = the outer diameter dimension D2, it is difficult to form stress concentration areas such as step boundaries on the valve body 11. Therefore, stress corrosion cracks caused by stress concentration can be prevented.

[0076] like Figure 10As shown, the check valve 1 is installed midway through the flow path of the fluid in the refrigeration cycle system 100. The refrigeration cycle system 100 is used, for example, in commercial air conditioners. This refrigeration cycle system 100 is formed by connecting an indoor heat exchanger 101, an outdoor heat exchanger 102, an expansion valve 103, a four-way valve 104, and three compressors 105 connected in parallel via piping. To prevent backflow of fluid to each compressor 105, the check valve 1 is connected between the discharge (high-pressure output) side of each compressor 105 and the four-way valve 104, with the compressor 105 as the inlet pipe 18 and the four-way valve 104 as the outlet pipe 19. During refrigeration operation, as shown by the solid arrow D101, the fluid, after being compressed by the compressor 105, reaches the outdoor heat exchanger 102 via the check valve 1 and the four-way valve 104. Then, after the fluid releases heat from the outdoor heat exchanger 102, it flows through the expansion valve 103 to the indoor heat exchanger 101, where it absorbs heat and returns to the compressor 105 through the four-way valve 104.

[0077] During heating operation, as shown by the dashed arrow D102, the fluid, after being compressed by the compressor 105, reaches the indoor heat exchanger 101 via check valve 1 and four-way valve 104. Then, after releasing heat from the indoor heat exchanger 101, the fluid flows to the outdoor heat exchanger 102 via expansion valve 103, absorbs heat from the outdoor heat exchanger 102, and then returns to the compressor 105 via four-way valve 104. The refrigeration cycle system 100 repeatedly performs the above cycle to provide indoor cooling or heating. Here, for example, under conditions of high cooling load, all three compressors 105 operate simultaneously, so all three check valves 1 are fully open. Furthermore, under conditions of low cooling load, operating only one compressor 105 is sufficient, so the other two compressors 105 do not operate. In this case, the pressure at the outlet pipe 19 of the two check valves 1 is higher than the pressure at the inlet pipe 18, resulting in backflow from the outlet pipe 19, and the two check valves 1 are closed.

[0078] According to the above-described embodiment, a protruding portion 15 is provided in the pressed-in portion 13 on the inner surface of the main body 10. The sealing portion S is formed by the tight contact between the pressed-in portion 33 of the valve seat member 20 and the protruding portion 15, thereby reliably preventing internal leakage of fluid flowing within the main body 10 to unexpected parts. This improves the sealing performance of the check valve 1 (valve device). Therefore, even when the fluid controlled by the check valve 1 is a high-pressure fluid, a higher sealing performance can be maintained compared to the conventional valve device structure where only the valve seat member is pressed into the valve core housing. Therefore, a check valve 1 with improved sealing performance can be provided.

[0079] Furthermore, in this embodiment, the protruding face 15 is formed by the pre-formed face 15a before the valve seat component 20 is pressed in, so that the pressing portion 33 of the valve seat component 20 comes into close contact with the pre-formed face 15a pre-formed in the main body 10 to form a sealing portion S. Therefore, compared with conventional valve devices that do not have the pre-formed face 15a in close contact with the pressing portion 33 of the valve seat component 20, even when using ultra-high pressure fluid as the control object of the check valve 1, internal leakage of fluid can be prevented. Moreover, the sealing performance of the check valve 1 can be maintained to a higher degree.

[0080] Furthermore, according to this embodiment, the protruding face 15a is formed with a predetermined angle θ1 relative to the axis L. Therefore, the protruding face 15 can be formed into various shapes, such as a conical shape inclined relative to the axis L of the main body 10, or a right-angled shape orthogonal to the axis L of the main body 10. Since the protruding face 15a can be set to have a predetermined angle θ1 relative to the axis L, by changing this angle, the tight contact state between the press-in portion 33 and the protruding face 15 can be appropriately changed according to conditions such as the material of the main body 10 and the valve seat component 20. Therefore, the sealing performance of the check valve 1 can be maintained to a higher degree. Furthermore, the shape of the protruding face 15 is not limited to a conical shape or a right-angled shape as described above; for example, a convex arc shape or a concave arc shape connecting the two ends of the conical portion can be formed instead of the inclined surface of the conical portion in the conical shape.

[0081] Furthermore, according to this embodiment, the main body 10 and the valve seat component 20 are cylindrical, and the pressed-in portion 13 is provided with a pressing-in portion 14, a protruding portion 15, and a small-diameter portion 16. Moreover, the pressing-in portion 14 is configured such that the inner diameter α1 of the valve seat component 20 before pressing in is smaller than the outer diameter β1 of the pressing portion 33 in the valve seat component 20 before pressing in. Furthermore, the small-diameter portion 16 has an inner diameter α2 that is less than or equal to the inner diameter α1 of the pressing-in portion 14, the end of the other side L2 of the protruding portion 15 is continuous with the pressing-in portion 14, and the end of one side L1 of the protruding portion 15 is continuous with the small-diameter portion 16. With this structure, the valve seat component 20 can be reliably pressed in relative to the main body 10, and a sealing portion S can be reliably formed between the protruding portion 15 and the pressing portion 33.

[0082] Furthermore, according to this embodiment, when the valve body 11 has a riveting portion 17, the thickness T1 of the small-diameter portion 16 is locally reduced at the riveting portion 17. However, since the original thickness T1 of the small-diameter portion 16 is larger than the thickness T2 of the press-in portion 14, the pressure resistance of the valve body 11 (body 10) will not be locally reduced. Therefore, cracks in the valve body 11 are easily prevented. By preventing these cracks, the risk of external fluid leakage can be reduced, and the reliability of the check valve 1 for ultra-high pressure fluids can be improved.

[0083] Furthermore, according to this embodiment, since the outer diameter D1 of the small diameter portion 16 is equal to the outer diameter D2 of the pressing portion 14, steps or the like caused by the difference in outer diameter will not form on the main body 10. Therefore, it is difficult to generate stress concentration areas such as the boundary portions of steps on the valve body 11 (main body 10). As a result, stress corrosion cracks caused by stress concentration can be easily prevented, improving the reliability of the check valve 1 for ultra-high pressure fluids.

[0084] Furthermore, according to this embodiment, the refrigeration cycle system 100 can be configured using a check valve 1 with improved sealing performance, thereby improving the energy efficiency of the refrigeration cycle system 100.

[0085] Furthermore, the embodiments described above are merely representative examples of the present invention, and the present invention is not limited thereto. That is, various modifications can be made to implement the invention without departing from the spirit of the invention. Even such modifications, as long as they possess the structure of the check valve 1 of the present invention, are naturally included within the scope of the present invention. For example, in the description of this embodiment, an inlet pipe 18 is provided on one side L1 of the valve body 11, and an outlet pipe 19 is provided on the other side L2. However, this configuration can also be reversed, and the inlet pipe 18 can be provided on the other side L2 of the valve body 11, and the outlet pipe 19 can be provided on one side L1 of the valve body 11.

[0086] Furthermore, the check valve 1 is merely one example of the valve device in this invention, and of course, the invention can be applied to other valve devices. For example, the invention can also be applied to a sliding switching valve or electric valve that has multiple valve ports within the valve body and controls the flow of fluid through the valve ports, a solenoid valve with a plunger and a solenoid coil, a pressure regulating valve that drives a pressure-sensitive component connected to the valve component according to pressure changes, and a manually operated valve with an operating part for moving the valve core forward and backward. Moreover, in this case, the valve device does not necessarily need to be used in the refrigeration cycle system 100; various devices for fluid control can be used.

[0087] Furthermore, in the above embodiment, the outer diameter dimension D1 of the small diameter portion 16 is set to be equal to the outer diameter dimension D2 of the pressing portion 14. Here, the outer diameter dimension D1 of the small diameter portion 16 being equal to the outer diameter dimension D2 of the pressing portion 14 means that the outer diameter dimension D2 of the pressing portion 14 is included in the range of 0% to +3% relative to the outer diameter dimension D1 of the small diameter portion 16.

[0088] Next, the second embodiment will be described. Figure 11 This is a cross-sectional view of the check valve 1A of the second embodiment, cut along the axis L. Figure 12 This is a cross-sectional view of the valve seat component 20A of the second embodiment, cut along the axis L. Figure 13 yes Figure 11An enlarged view of the main components of the check valve 1A shown. Figure 11 As shown, in the check valve 1A of the second embodiment, the aforementioned riveting portion 17 is omitted from the L1 portion on one side of the press-in portion 13A. Furthermore, as... Figure 12 As shown, in the check valve 1A, the annular recess 34 that engages with the aforementioned riveting portion 17 is omitted from the L1 portion on one side of the press-in portion 33A of the valve seat component 20A. In a check valve 1A configured in this way, as... Figure 13 As shown, a pressing amount portion 14A is formed in the pressing portion 13A. The pressing amount portion 14A corresponds to the pressing amount portion 14 in the above embodiment. Furthermore, the pressing amount portion 14A constitutes an existing surface formed before the pressing valve seat component 20A.

[0089] In the second embodiment, the press-in portion 14A of the existing face is formed by plastic processing of the inner surface of the main body 10A. Through this plastic processing, the thickness T2 of the press-in portion 14A becomes smaller than the thickness T1 of the small-diameter portion 16A. By plastic processing to form the press-in portion 14A with a thickness T2 smaller than the thickness T1 of the small-diameter portion 16A, the hardness of the press-in portion 14A is higher than that of the small-diameter portion 16A, making it difficult for the press-in portion 14A to deform. Therefore, even if the structure within the main body 10A undergoes repeated changes such as expansion or contraction due to changes in pressure and temperature, the holding strength of the main body 10A for the press-in portion 33A of the valve seat component 20A can be maintained at a high level, ensuring stable sealing of the sealing portion S. Furthermore, according to this structure, even without providing the riveting portion 17 in the main body 10A, the holding force for the press-in portion 33A of the valve seat component 20A can be maintained. Therefore, for example, the repeated contact (impact) between the valve core 50 and the valve limiting member 43 during valve opening can improve the anti-disengagement strength of the valve seat component 20A. In this way, the pressing portion 14A constitutes a retaining force strengthening portion that enhances the retaining force of the pressed portion 13A.

[0090] Furthermore, any plastic processing method that can achieve work hardening can be appropriately selected. For example, although not shown, a cylinder extending along the axis L can be formed using a metal material constituting the main body 10A, and a rod-shaped clamp or the like can be inserted into the cylinder. A portion of the outer wall of the cylinder can then be pressed from the radially outward to the radially inward direction using a spinning process or the like. In this way, the outer peripheral shape of the rod-shaped clamp is transferred to the inner peripheral surface of the cylinder, forming the press-in portion 14A, etc.

[0091] Next, the third embodiment will be described. Figure 14 This is a cross-sectional view of the check valve 1B of the third embodiment, cut along the axis L. Figure 15 (A) is a cross-sectional view of the valve seat component 20B of the third embodiment, cut along the axis L. Figure 15 (B) is Figure 14 An enlarged sectional view of region I in the diagram. Figure 16 (A) to (D) are side views of the main body 10A, main body 10B, and main body 10C used to show the changes of the riveting part 17B and the riveting part 17C. Figure 17 (A) is Figure 14 Enlarged view of region II in the image. Figure 17 (B) is Figure 15 AA line sectional view in the middle, Figure 17 (C) is a cross-sectional view showing another embodiment of the oil inlet 37. (e.g.) Figure 14 As shown, the check valve 1B of the third embodiment has a large-diameter portion 12B and a press-in portion 13B on the inner circumferential surface of the main body 10B. The press-in portion 13B has a press-in amount portion 14B, a protruding portion 15B and a small-diameter portion 16B from the other side L2 toward one side L1.

[0092] The aforementioned large-diameter portion 12B, pressed-in portion 13B, pressed-in amount portion 14B, protruding portion 15B, and small-diameter portion 16B correspond to the aforementioned large-diameter portion 12, pressed-in portion 13, pressed-in amount portion 14, protruding portion 15, and small-diameter portion 16. For example... Figure 14 As shown, in the main body 10B, a riveting portion 17B is formed on one side L1 portion of the pressed-in portion 13B, which engages with the pressed-in valve seat component 20B. The riveting portion 17B is formed by riveting one side L1 portion of the main body 10B from the radially outward to the radially inward direction. Figure 15 As shown in (B), the riveting portion 17B has an arc-shaped protrusion centered on the intersection of an imaginary line c1 along the outer peripheral surface of the main body 10B and an imaginary line c2 orthogonal to the imaginary line c1, and its front end constitutes a riveting protrusion 17B1. This riveting protrusion 17B1 engages with the corner 34a of the valve seat component 20B described below. Furthermore, in this embodiment, although the outer peripheral surface of the main body 10B overlaps with the imaginary line c1, since the position of the imaginary line c1 varies according to the shape of the riveting portion 17, the outer peripheral surface of the main body 10B may not overlap with the imaginary line c1.

[0093] Next, the valve seat component 20B will be described. For example... Figure 15 As shown in (A), an inwardly recessed annular recess 34B is formed on one side L1 of the valve seat component 20B and the press-in portion 33B. The end of one side L1 of the annular recess 34B forms a corner 34a with a surface 34a1 facing the other side L2 of the valve seat component 20B. Figure 15As shown in (B), after the valve seat component 20B is pressed into the main body 10B and the riveting portion 17B is formed, the riveting protrusion 17B1 engages with a portion of the corner portion 34a. Therefore, compared to a structure where the riveting protrusion 17B1 only abuts against the corner portion 34a, the valve seat component 20B is less likely to loosen relative to the main body 10B. Thus, the holding force of the main body 10B on the valve seat component 20B can be further improved, thereby further enhancing the anti-loosening strength of the valve seat component 20B.

[0094] Furthermore, at this time, the valve seat component 20B and the main body 10B are closer together in the snap-fit ​​direction. As a result, the inclined surface 33b of the press-fit portion 33B constituting the sealing portion S comes into closer contact with the protruding surface 15B of the main body 10B, increasing the surface pressure of the sealing portion S. Therefore, the sealing performance of the sealing portion S is further improved. Consequently, this snap-fit ​​portion can form a working fluid leakage prevention part that suppresses fluid leakage, thus suppressing internal fluid leakage. Figure 15 In (B), the symbol V indicates the amount by which the riveting protrusion 17B1 engages with the corner portion 34a. This engagement amount is indicated by the distance between a straight line C1 and a straight line C2 parallel to and connected to the riveting protrusion 17B1, wherein the straight line C1 is orthogonal to an imaginary line c3 drawn from the intersection of the aforementioned imaginary lines c1 and c2 toward the vertex of the corner portion 34a. This engagement amount V is preferably about 1% to 20% of the thickness dimension T3 of the small diameter portion 16B. In this way, the engagement portion (working fluid leakage prevention portion) engaging with the corner portion 34a can appropriately maintain a sealing performance that prevents internal leakage, and can suppress deformation of the valve seat component 20B when engaging with the corner portion 34a.

[0095] Furthermore, in the axial direction L, the dimension from the end of one side L1 of the valve seat component 20B to the corner 34a is set as dimension α7. And the dimension from the corner 34a to the end of the other side L2 of the riveting protrusion 17B1 (the boundary between the riveting protrusion 17B1 and the small-diameter portion 16B) is set as dimension α8. In this case, dimension α7 is preferably at least 0.5 times dimension α8. Therefore, in the valve seat component 20B, the dimension in the axial direction L from the portion forming the corner 34a to the end of one side L1 can be sufficiently ensured, thereby ensuring the strength of the one side L1 portion of the valve seat component 20B. Therefore, deformation of the one side L1 portion of the valve seat component 20B can be suppressed, thereby further improving the anti-detachment strength of the valve seat component 20B when the riveting protrusion 17B1 engages with the corner 34a.

[0096] Furthermore, the rivet 17B that engages with the corner portion 34a can also be achieved by... Figure 16 As shown in (A), the outer periphery of the main body 10A without the riveted portion 17 is rolled and riveted, while... Figure 16 As shown in (B), it is formed around the entire circumference of the axis L, but more preferably as shown in (B). Figure 16 As shown in (C), a pressure point is formed at the location corresponding to the small diameter portion 16B by stamping riveting. In this case, the riveting protrusion 17B1 is composed of the front end of the riveting portion 17B that protrudes inward into the body 10B by being formed by stamping riveting. Accordingly, by forming the riveting portion 17B using stamping riveting, the stress generated in the riveting portion 17B can be reduced compared to the so-called roll riveting structure that rivets the entire circumference of the body 10B.

[0097] Therefore, cracks in the main body 10B and external leakage of fluid caused by cracks can be suppressed. Furthermore, even if the riveted portion 17B, formed by stamping and riveting, is formed in only one location, the retaining force of the valve seat component 20B can be improved. However, from the viewpoint of ensuring a balance of strength throughout the entire circumference of the main body 10B, it is more preferable, for example, to form it at equal intervals in four or eight locations along the circumference of the main body 10B.

[0098] Then, as Figure 15 As shown in (A), a flange portion 35B is formed at the end of the press-in portion 33B of the valve seat component 20B on the other side L2, protruding radially outward toward the inner surface of the body 10B. Figure 17 As shown in (A), with the valve seat component 20B pressed into the main body 10B, the flange portion 35B abuts against the boundary portion 10B1 between the large-diameter portion 12B and the pressed-in portion 14B on the inner surface of the main body 10B. At this time, a space is formed between the main body 10B and the valve seat component 20B, enclosed by the flange portion 35B, the pressed-in portion 33B (the portion of the valve seat component 20B excluding the flange portion 35B), and the pressed-in portion 14B of the main body 10B. This space constitutes an oil reservoir 36 capable of accumulating oil 60 contained in the fluid flowing to the check valve 1B. Moreover, as... Figure 17 As shown in (B), an oil inlet portion 37 is formed in the flange portion 35B to communicate with the interior of the oil storage portion 36 and the main body 10B. The oil inlet portion 37 is formed by the gap between the valve seat component 20B, which is formed by cutting a portion of the outer peripheral surface of the flange portion 35B, which is formed in the shape of an annular shape, and the inner surface of the main body 10B.

[0099] Furthermore, in the third embodiment, although the oil inlet portion 37 is formed by a cut, the structure of the oil inlet portion 37 is not limited to this. It can also be as follows: Figure 17As shown in (C), a groove 38 is formed inwardly on a portion of the outer peripheral surface of the annular flange 35B, extending through it in the axial direction L to form an oil inlet. In this structure, oil 60 contained in the fluid flowing within the main body 10B enters the oil reservoir 36 through the oil inlet 37 and accumulates there. The accumulated oil 60 is supplied between the valve seat component 20B and the main body 10B via capillary action. Therefore, for example, assuming a small gap or scratch exists between the press-in portion 14B of the main body 10B and the press-in portion 33B of the valve seat component 20B, the oil 60 supplied to this gap or scratch can more reliably suppress internal fluid leakage. That is, similar to the snap-in portion 34a described above, the oil reservoir 36 and the oil inlet 37 constitute a working fluid leakage prevention part that suppresses fluid leakage.

[0100] And, as Figure 17 As shown in (A), the oil 60 accumulated in the oil reservoir 36 is difficult to move to the other side L2 because the flange portion 35B abuts against the flange abutment portion 35B1 of the main body 10B. Therefore, compared with the structure in which the oil reservoir is provided only by creating a gap between the valve seat member 20B and the main body 10B, the following situation can be suppressed: that is, the so-called jetting effect of oil 60 being drawn out of the oil reservoir 36 by the flow of fluid around the oil reservoir 36 can be prevented.

[0101] Next, the fourth embodiment will be described. Figure 18 This is a cross-sectional view of the check valve 1C of the fourth embodiment, cut along the axis L. Figure 19 yes Figure 18 An enlarged view of region III. A riveting portion 17C is formed on one side L1 of the large-diameter portion 12C in the check valve 1C and the body 10C. This riveting portion 17C is preferably formed by... Figure 16 As shown in (A), the outer periphery of the body 10A without the riveted portion 17C is as follows: Figure 16 As shown in (D), stamping and riveting are performed to form the pressure point. For example... Figure 19 As shown, the front end of the riveting portion 17C forms a riveting protrusion 17C1. The riveting portion 17C corresponds to the riveting portion 17B described above, and the riveting protrusion 17C1 corresponds to the riveting protrusion 17B1 described above. Furthermore, in the check valve 1C, Figure 19 The outer peripheral edge of the flange portion 35C of the valve seat component 20C shown forms a corner portion 35C1 with a surface 39 facing the other end L2 of the valve seat component 20C. The riveting protrusion 17C1 is engaged with the corner portion 35C1.

[0102] Figure 19In the diagram, symbol V2 indicates the amount of engagement of the riveting protrusion 17C1 into the corner portion 35C1. This engagement amount is indicated by the distance between a straight line C3 and a straight line C4 parallel to and connected to the riveting protrusion 17C1, wherein the straight line C3 is orthogonal to an imaginary line c3 drawn from the intersection of an imaginary line c1 along the outer peripheral surface of the body 10C and an imaginary line c2 orthogonal to the imaginary line c1 toward the vertex of the corner portion 35C1. This engagement amount V2 is preferably about 1% to 20% of the thickness dimension T3 of the large diameter portion 12C. In this way, the engagement portion (working fluid leakage prevention portion) that can engage with the corner portion 35C1 by the riveting protrusion 17C1 can properly maintain a sealing performance that can prevent internal leakage, can suppress deformation of the valve seat component 20C when engaging with the corner portion 35C1, and can improve the anti-detachment strength of the valve seat component 20C.

[0103] Furthermore, according to the fourth embodiment, by engaging the riveting protrusion 17C1 with the corner 35C1 of the flange portion 35C in the valve seat component 20C, a working fluid leakage prevention portion can be formed. Therefore, it is unnecessary to form the corner 34a of the annular recess 34B, and the annular recess 34B can be omitted. Thus, compared with the structure that forms the annular recess 34B, the dimension of the valve seat component 20C in the axial direction L can be reduced. As a result, the check valve 1C can be miniaturized, and the overall cost can be reduced.

[0104] Symbol Explanation

[0105] L1—One side, L2—The other side, S—Sealing part, 1—Check valve (valve device), 10—Main body, 13—Pressed part, 15—Protruding part, 20—Valve seat component, 31—Valve port, 33—Pressed part, 50—Valve core.

Claims

1. A valve device comprising a cylindrical body extending from one side to the other and through which fluid flows, a valve seat member pressed into the body, and a valve core for opening and closing a valve port disposed on the valve seat member, characterized in that it comprises: A press-in portion is provided on the outer surface of the aforementioned valve seat component; and The pressed-in portion is disposed on the inner surface of the main body, and the pressed-in portion slides into contact with the pressed-in portion from the other side to the other side. A protruding surface is provided at a position on one side closer to the other side of the aforementioned pressed-in portion, protruding inward toward the main body. The tight contact between the aforementioned press-in portion and the aforementioned protruding surface portion constitutes a sealing portion that prevents leakage of the aforementioned fluid.

2. The valve device according to claim 1, characterized in that, The aforementioned protruding face is formed by an existing face that was formed before the valve seat component was pressed in.

3. The valve device according to claim 1, characterized in that, The aforementioned protruding face is formed at a predetermined angle relative to the axis of the aforementioned body extending from the aforementioned side to the aforementioned other side.

4. The valve device according to claim 1, characterized in that, The aforementioned main body and valve seat component are cylindrical. The aforementioned pressed-in portion includes a pressing-in portion disposed on the other side, a small-diameter portion disposed on one side, and a protruding surface portion disposed between the pressing-in portion and the small-diameter portion. The inner diameter of the valve seat component before pressing in the aforementioned pressing-in portion is smaller than the outer diameter of the pressing-in portion in the aforementioned valve seat component before pressing in. The aforementioned small-diameter portion has an inner diameter dimension that is less than or equal to the inner diameter dimension of the aforementioned press-in portion. The end of the protruding face on the other side is continuous with the indentation portion, and the end of the protruding face on the other side is continuous with the small diameter portion.

5. The valve device according to claim 4, characterized in that, On the other side of the aforementioned pressing portion, there is a large-diameter portion with an inner diameter larger than that of the aforementioned pressing portion. The valve seat component is provided with a flange portion that protrudes toward the inner surface of the main body and abuts against the boundary portion between the large-diameter portion and the press-in portion on the inner surface. The space enclosed by the flange portion and the portion other than the flange portion in the valve seat component, and the pressurization portion in the main body constitutes an oil storage section capable of accumulating oil contained in the fluid. The flange portion is provided with an oil inlet portion that connects the oil storage portion to the interior of the main body. The aforementioned oil storage section and the aforementioned oil inlet section constitute a working fluid leakage prevention section that suppresses the leakage of the aforementioned fluid.

6. The valve device according to claim 4, characterized in that, The aforementioned main body has a retaining force reinforcing part that strengthens the retaining force of the pressed-in part. The aforementioned retaining force reinforcing portion is composed of the aforementioned indentation portion that has undergone plastic processing. The thickness of the aforementioned indentation portion is smaller than the thickness of the aforementioned small diameter portion.

7. The valve device according to claim 4, characterized in that, The outer diameter of the aforementioned small diameter portion is equal to the outer diameter of the aforementioned pressing portion.

8. The valve device according to claim 1, characterized in that, A corner portion having a surface facing the other end of the valve seat component is provided on the outer periphery of the aforementioned valve seat component. The aforementioned main body is provided with a riveting part that faces inward for riveting. The aforementioned riveting portion is provided with a riveting protrusion that engages with the aforementioned corner portion.

9. The valve device according to claim 8, characterized in that, The aforementioned riveting protrusion is formed by the front end of the aforementioned riveting portion, which is formed on the outer periphery of the aforementioned body by stamping and riveting and protrudes into the aforementioned body.

10. The valve device according to claim 8, characterized in that, The aforementioned riveting protrusion engages with at least a portion of the aforementioned corner portion, and the engaged portion constitutes a working fluid leakage prevention part that suppresses the leakage of the aforementioned fluid.

11. The valve device according to claim 8, characterized in that, An inwardly recessed annular recess is provided on one side of the aforementioned valve seat component. The end portion of the aforementioned annular recess on one side constitutes the aforementioned corner portion. In the axial direction of the main body, the dimension from the end of the valve seat component on one side to the corner is at least 0.5 times the dimension from the corner to the end of the riveting protrusion on the other side.

12. A check valve, characterized in that, It is composed of the valve device according to any one of claims 1 to 11.

13. A refrigeration cycle system, characterized in that, The check valve as described in claim 12 is provided.

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