Valve device

Abstract

To provide a valve device for which reliability has been improved.SOLUTION: A plurality of orifice passages 121 is formed by providing the inner surface 122 of a valve member 115 with grooves which extend in the radial direction of a cylinder 101. Due to this configuration, even if foreign matter clogs some of the orifice passages 121, the area of the flow path can be ensured by the remaining orifice passages 121, and the reliability of the valve device 1 can be increased.SELECTED DRAWING: Figure 3

Description

[Technical Field]

[0001] The present invention relates to a valve device applied to an automatic height adjustment valve for a railway vehicle. [Background Art]

[0002] Patent Document 1 discloses a leveling valve 100 (valve device) for a railway vehicle that includes an oil damper 60 that generates a predetermined operation delay time from when a displacement input is applied to a lever 4 to when an air supply valve 31 and an exhaust valve 32 open. The oil damper 60 of this leveling valve 100 is provided with orifices 69a and 69b that apply resistance to the flow of hydraulic oil discharged from a first damper chamber 64a and a second damper chamber 64b to an oil chamber 12 when the first damper chamber 64a and the second damper chamber 64b are compressed as a piston 61 moves. [Prior Art Documents] [Patent Documents]

[0003] [Patent Document 1] Japanese Unexamined Patent Application Publication No. 2013-173438 [Summary of the Invention] [Problem to be Solved by the Invention]

[0004] In the valve device described in Patent Document 1, since the passage area of the orifice provided in the center of the valve is small, if foreign matter clogs the orifice, the passage area of the orifice will decrease and the resistance of the piston will increase. This causes a delay in air supply or exhaust of the valve device, prolonging the time it takes for the horizontal lever of the valve device to return to the neutral position, and furthermore the time it takes for the vehicle height to return to the fixed position, which may reduce the running stability of the railway vehicle.

[0005] An object of the present invention is to improve the reliability of a valve device. [Means for Solving the Problem]

[0006] To solve the above problems, the valve device of the present invention is a valve device provided between a fluid source or the outside and a fluid-operated device, which controls the supply and discharge of fluid to the fluid-operated device, comprising: a housing in which an oil chamber is formed; a cylinder provided in the oil chamber; a piston provided in the cylinder and defining a damper chamber; a communication passage provided on the piston and connecting the damper chamber and the oil chamber; and a valve provided on the piston and controlling the flow of working fluid through the communication passage, wherein the valve is provided protruding from the piston and has an annular seat portion in which the communication passage opens inside the annular seat portion; a valve member that abuts the seat portion so as to be able to seat and detach from it; a biasing member that biases the valve member in the closing direction; and an orifice passage that restricts the flow path of working fluid between the damper chamber and the communication passage, wherein the flow path area inside the seat portion of the orifice passage is smaller than the flow path area outside the seat portion. The valve member is formed such that it comprises a first valve member that abuts against the seat portion and a second valve member positioned between the first valve member and the biasing member, and the orifice passage comprises a plurality of first passages formed between the first valve member and the second valve member and a second passage provided in the first valve member that connects the plurality of first passages and the connecting passage. It is characterized by the following: [Effects of the Invention]

[0007] According to one embodiment of the present invention, blockage of the orifice passage can be suppressed, thereby increasing the reliability of the valve device. [Brief explanation of the drawing]

[0008] [Figure 1] This is an explanatory diagram of the first embodiment, and is a conceptual diagram of a system including a valve device. [Figure 2] This is a cross-sectional view of a valve device according to the first embodiment. [Figure 3] This is an explanatory diagram of an oil damper according to the first embodiment. [Figure 4] This is an explanatory diagram of the oil damper according to the second embodiment. [Figure 5] This is an explanatory diagram of the oil damper according to the third embodiment. [Figure 6] This is an explanatory diagram of a valve member according to the first embodiment. [Figure 7] This is an explanatory diagram of a valve member according to the second embodiment. [Figure 8] This is an explanatory diagram of the valve member according to the third embodiment. [Modes for carrying out the invention]

[0009] (First Embodiment) A first embodiment of the present invention will be described with reference to the attached figures. Figure 1 is a conceptual diagram of system 11, including valve device 1 (automatic height adjustment valve for railway vehicles). For convenience, the vertical direction in Figure 1 will be referred to as the vertical direction. Similarly, the left-right direction in Figure 1 will be referred to as the left-right direction.

[0010] As shown in Figure 1, the system 11 includes a compressor 12 (fluid source), an air spring 13 (fluid-operated device), and a passage 14 that constitutes a flow path for air (fluid) between the compressor 12 and the air spring 13. The passage 14 is provided with a valve device 1 that automatically adjusts the height of the car body 16 relative to the bogie 15. The valve device 1 includes a housing 2 attached to the car body 16 and a driven shaft 3 located in the center of the housing 2. The driven shaft 3 is connected to the bogie 15 via a horizontal lever 17 and a connecting bar 18.

[0011] Referring to Figures 1 and 2, when the vehicle height changes, that is, when the air spring 13 is compressed or extended and the vehicle body 16 is displaced vertically relative to the bogie 15, the valve device 1 converts this displacement into rotational motion of the driven shaft 3. Here, when the vehicle height decreases, that is, when the air spring 13 is compressed, the horizontal lever 17 rotates counterclockwise around the driven shaft 3 from its neutral position (see Figure 1). As a result, the driven shaft 3 rotates counterclockwise in Figure 1 in conjunction with the horizontal lever 17, and as a result the air supply valve 21 opens, and the passage 14 between the compressor 12 and the air spring 13 is opened.

[0012] When the air intake valve 21 opens and the passage 14 is opened, compressed air from the compressor 12 is supplied to the air spring 13, causing the air spring 13 to extend. When the air spring 13 extends, the horizontal lever 17 rotates clockwise around the driven shaft 3 in the direction shown in Figure 1, and the driven shaft 3 rotates clockwise in the direction shown in Figure 1 in conjunction with the horizontal lever 17. Then, when the vehicle height reaches the standard height, that is, when the horizontal lever 17 returns to the neutral position (see Figure 1), the air intake valve 21 closes and the passage 14 is blocked.

[0013] On the other hand, when the vehicle height rises, that is, when the air spring 13 extends, the horizontal lever 17 rotates clockwise around the driven shaft 3 from its neutral position (see Figure 1). As a result, the driven shaft 3 rotates clockwise in Figure 1 in conjunction with the horizontal lever 17, the exhaust valve 81 opens, and the air spring 13 and the exhaust port 19 (see Figure 1) come into contact.

[0014] When the exhaust valve 81 opens and the air spring 13 and the exhaust port 19 are connected, the air stored in the air spring 13 is discharged into the atmosphere, and the air spring 13 is compressed. When the air spring 13 is compressed, the horizontal lever 17 rotates counterclockwise around the driven shaft 3 in the direction shown in Figure 1, and the driven shaft 3 rotates counterclockwise in the direction shown in Figure 1 in conjunction with the horizontal lever 17. Then, when the vehicle height returns to the standard height, that is, when the horizontal lever 17 returns to the neutral position (see Figure 1), the exhaust valve 81 closes, and the communication between the air spring 13 and the exhaust port 19 (atmosphere) is cut off.

[0015] Thus, in system 11, when the horizontal lever 17 rotates around the driven shaft 3 in accordance with the relative displacement of the car body 16 relative to the bogie 15, the driven shaft 3 rotates clockwise or counterclockwise in conjunction with the horizontal lever 17. The valve device 1 connects the air spring 13 to the compressor 12 (fluid source) or the exhaust port 19 (atmosphere) according to the direction of rotation of the driven shaft 3 (the direction of rotation of the horizontal lever 17). As a result, the relative displacement of the car body 16 relative to the bogie 15 is automatically adjusted, and the vehicle height is maintained at the reference height.

[0016] FIG. 2 is a cross-sectional view of the valve device 1. As shown in FIG. 2, the housing 2 is provided with a driven shaft 3 that is the rotation shaft of the horizontal lever 17. The driven shaft 3 is provided with an actuating arm 4 and a torsion spring 5. When the actuating arm 4 is rotated about the driven shaft 3 toward the air supply side (the "counterclockwise direction" in FIG. 2) or the exhaust side (the "clockwise direction" in FIG. 2), the torsion spring 5 generates an urging force (spring force) that restores the actuating arm 4 to the neutral position (see FIG. 2). A non-return valve 6 is provided at the upper center of the housing 2.

[0017] An air supply valve 21 is provided on the upper left side of the housing 2. The air supply valve 21 has a case 24 attached to a case hole 23 provided in the housing 2. The case hole 23 has a large-diameter hole portion 25 whose left end opens to the left side surface 22 of the housing 2, and a small-diameter hole portion 26 whose right end opens to the central oil chamber 7 of the housing 2. A small-diameter shaft portion 28 of the case 24 is fitted into the small-diameter hole portion 26 of the case hole 23. A large-diameter shaft portion 27 of the case 24 is fixed to the large-diameter hole portion 25 of the case hole 23.

[0018] An annular flow path 29 is provided between the small-diameter shaft portion 28 of the case 24 and the large-diameter hole portion 25 of the case hole 23. Further, an annular flow path 30 is provided between the small-diameter shaft portion 28 of the case 24 and the small-diameter hole portion 26 of the case hole 23. The annular flow path 30 is sealed by seal rings 31 and 32 provided on the small-diameter shaft portion 28 of the case 24. Further, the annular flow path 29 is sealed by seal rings 32 and 33.

[0019] A valve stem 44 coaxial with respect to the case hole 23 and the case 24 is provided in the hollow portion of the case 24. The valve stem 44 is slidably fitted into the first hole portion 35 of the case 24. The first hole portion 35 of the case 24 is sealed relative to the oil chamber 7 by a seal ring 46 provided on the small-diameter shaft portion 28 of the case 24. A distal end portion 45 of the valve stem 44 protrudes into the oil chamber 7 from the end surface on the inner side of the case 24 (the "right side" in FIG. 2). The valve stem 44 moves in the axial direction (horizontal direction) in conjunction with the rotation of the actuating arm 4 when the spherical surface of the distal end portion 45 abuts against the actuating arm 4.

[0020] The hollow portion of case 24 is provided with a second hole 36 at the bottom, through which the left end of the first hole 35 opens. The second hole 36 is connected to the annular flow channel 30 by multiple passages 37 (shown as "2" in Figure 2) provided on the small-diameter shaft portion 28 of case 24. The hollow portion of case 24 is also provided with a third hole 38, through which the left end of the second hole 36 opens. The third hole 38 is connected to the annular flow channel 29 by multiple passages 39 (shown as "2" in Figure 2) provided on the small-diameter shaft portion 28 of case 24. The hole diameters of the hollow portion of case 24 increase in the order of the first hole 35, the second hole 36, and the third hole 38.

[0021] An air supply port 51 is mounted on the left end of the case 24. The third hole 38 is sealed to the atmosphere by a seal ring 46 provided on the air supply port 51. The air supply port 51 is prevented from coming out of the case 24 by a retaining ring 53 attached to the case 24. The other end of a passage 14A (see Figure 1), one end of which is connected to a compressor 12 (fluid source), is connected to the air supply port 51. The air supply port 51 is also connected to an annular flow path 29 via a passage (not shown) provided in the housing 2.

[0022] The air supply valve 21 is provided with a valve 41 that connects or disconnects the compressor 12 (fluid source) and the air spring 13 (fluid-operated device) according to the movement of the valve stem 44. The valve 41 has an annular seat portion 42 with the left end of the second hole portion 36 opening to the inside, and a valve body 43 that abuts against the seat portion 42 so as to be able to seat and unseat. The valve body 43 is integrated with the valve stem 44, but may be configured as a separate part. The valve body 43 is biased in the closing direction (to the right in Figure 2) by a valve spring 47 provided between the valve body 43 and the air supply side port portion 51.

[0023] An exhaust valve 61 is provided on the upper right side of the housing 2. The exhaust valve 61 has a case 64 that is attached to a case hole 63 provided in the housing 2. The case hole 63 has a large-diameter hole 65 at its right end that opens to the right side surface 62 of the housing 2, and a small-diameter hole 66 at its left end that opens to the oil chamber 7 in the center of the housing 2. The small-diameter shaft portion 68 of the case 64 is fitted into the small-diameter hole 66 of the case hole 63. The large-diameter shaft portion 67 of the case 64 is fixed to the large-diameter hole 65 of the case hole 63.

[0024] An annular channel 69 is provided between the small-diameter shaft portion 68 of case 64 and the large-diameter hole portion 65 of case hole 63. An annular channel 70 is also provided between the small-diameter shaft portion 68 of case 64 and the small-diameter hole portion 66 of case hole 63. The annular channel 70 is sealed by seal rings 71 and 72 provided on the small-diameter shaft portion 68 of case 64. The annular channel 69 is sealed by seal rings 72 and 73.

[0025] A valve stem 84 is provided in the hollow portion of the case 64, coaxial with the case 64 and containing a case hole 63. The valve stem 84 is slidably fitted into the first hole 75 of the case 64. The first hole 75 of the case 64 is sealed from the oil chamber 7 by a seal ring 86 provided on the small diameter shaft portion 68 of the case 64. The tip 85 of the valve stem 84 protrudes into the oil chamber 7 from the inner end face (left side in Figure 2) of the case 64. The valve stem 84 moves axially (horizontally) in conjunction with the rotation of the operating arm 4 as the spherical surface of the tip 85 abuts against the operating arm 4.

[0026] The hollow portion of case 64 is provided with a second hole 76 at the bottom, through which the right end of the first hole 75 opens. The second hole 76 is connected to the annular flow channel 70 by multiple passages 77 (shown as "2" in Figure 2) provided on the small-diameter shaft portion 68 of case 64. The hollow portion of case 64 is also provided with a third hole 78, through which the right end of the second hole 76 opens. The third hole 78 is connected to the annular flow channel 69 by multiple passages 79 (shown as "2" in Figure 2) provided on the small-diameter shaft portion 68 of case 64. The hole diameters of the hollow portion of case 64 increase in the order of the first hole 75, the second hole 76, and the third hole 78.

[0027] An exhaust port portion 91 is mounted on the right end of the case 64. The third hole portion 78 is sealed to the atmosphere by a seal ring 92 provided on the exhaust port portion 91. The exhaust port portion 91 is prevented from coming out of the case 64 by a retaining ring 93 attached to the case 64. The other end of a passage 14B (see Figure 1), one end of which is connected to an air spring 13 (fluid-operated device), is connected to the exhaust port portion 91. The exhaust port portion 91 is also connected to an exhaust port 19 via a passage (not shown) provided in the housing 2.

[0028] The exhaust valve 61 is provided with a valve 81 that connects or disconnects the compressor 12 (fluid source) and the air spring 13 (fluid-operated device) according to the movement of the valve stem 84. The valve 81 has an annular seat portion 82 with the right end of the second hole portion 76 opening to the inside, and a valve body 83 that abuts against the seat portion 82 so as to be able to seat and unseat. The valve body 83 is integrated with the valve stem 84 but may be configured as a separate part. The valve body 83 is biased in the closing direction (leftward in Figure 2) by a valve spring 87 provided between the valve body 83 and the exhaust port portion 91.

[0029] An oil damper 100 is provided at the bottom of the housing 2 to generate a predetermined operating delay between the displacement input to the horizontal lever 17 and the opening of the air intake valve 21 and the exhaust valve 61. As shown in Figure 2, the oil damper 100 is configured symmetrically, so only the configuration of the side that generates an operating delay for the opening of the air intake valve 21 (the "right side" in Figure 2) will be explained, and the configuration of the side that generates an operating delay for the opening of the exhaust valve 61 (the "left side" in Figure 2) will be omitted. In the configuration of the left side of the oil damper 100, the symbols of each element corresponding to the configuration of the right side of the oil damper 100 plus "30" will be indicated in the drawing as appropriate.

[0030] As shown in Figures 2 and 3, the oil damper 100 has a cylinder 101 provided in the oil chamber 7. The axis of the cylinder 101 is positioned parallel to the axes of the case holes 23 and 63. A piston 102 is slidably fitted into the cylinder 101. The piston 102 is connected to the left piston 132 by a connecting rod 103. The connecting rod 103 is connected to the lower end of the operating arm 4 via a roller (not shown).

[0031] The right end opening of the cylinder 101 is closed by a plug 104. A damper chamber 105 filled with hydraulic fluid is provided between the piston 102 and the plug 104. The damper chamber 105 is sealed to the atmosphere by a seal ring 106 provided on the plug 104. The plug 104 is prevented from coming out of the housing 2 by a retaining ring 107 attached to the housing 2.

[0032] The housing 2 is provided with a through hole 124 that connects the outside of the housing 2 to the inside of the cylinder 101, and a communication passage 125 that connects the inside of the cylinder 101 to the oil chamber 7. The through hole 124 and the communication passage 125 are provided coaxially. The through hole 124 is normally closed by a closing member 126 made of a sphere. When the operating arm 4 is in the neutral position (see Figure 2), the lower end opening of the communication passage 125 is closed by the piston 102.

[0033] The piston 102 is provided with a recess 109 that opens into the end face 108 of the piston 102. The recess 109 has a circular cross-section (see Figure 6) formed by a plane perpendicular to the axis of the piston 102. That is, the recess 109 has an inner cylindrical surface 110. A communication passage 112 that connects the damper chamber 105 and the oil chamber 7 opens in the center of the circular bottom surface 111 of the recess 109. The communication passage 112 has a circular cross-section (see Figure 6) formed by a plane perpendicular to the axis of the piston 102. That is, the communication passage 112 has a circular flow path.

[0034] A valve 113 is provided in the recess 109 of the piston 102 to control the flow of hydraulic fluid between the damper chamber 105 and the oil chamber 7. The valve 113 has an annular seat portion 114 that protrudes from the bottom surface 111 of the recess 109 of the piston 102. The seat portion 114 has a rectangular cross-section formed by a plane containing the axis of the piston 102 (axial plane). A communication passage 112 opens on the inside (center) of the seat portion 114. The cylinder 102, the communication passage 112, and the seat portion 114 are arranged coaxially.

[0035] The valve 113 has a valve member 115 that abuts against the seat portion 114 so as to be able to seat and release from it. The valve member 115 is formed in the shape of a plate of a certain thickness. The valve member 115 has four end faces 116 located on each side of a square whose diagonal intersections lie on the axis of the cylinder 101 in a plan view (see Figure 6). In addition, the valve member 115 has four sliding surfaces 118 at its four corners that slidably abut against the inner circumferential surface 117 of the cylinder 102. The four sliding surfaces 118 are located on the same circle (the inner circumferential surface 117 of the cylinder 101) in a plan view, which has a larger diameter than the inscribed circle of the square including the end faces 116 and a smaller diameter than the circumscribed circle. For convenience, the intersection of the diagonals of the square including the end faces 116 is referred to as the center of the valve member 115.

[0036] Valve 113 has a valve spring 119 (biasing member) that biases the valve member 115 in the closing direction (leftward in Figure 3), that is, in the direction that presses the valve member 115 against the seat portion 114. The valve spring 119 is a coil spring (conical spring) that is compressed and provided between the valve member 115 and a retaining ring 120 attached to a recess 109 of the piston 102. Valve 113 has multiple (four in the first embodiment) orifice passages 121 that constantly connect the damper chamber 105 and the communication passage 112. The orifice passage 121 acts as a throttle valve that provides resistance to the flow of hydraulic fluid from the damper chamber 105 to the communication passage 112 when the piston 102 moves to the rightward in Figure 3 and the hydraulic fluid in the damper chamber 105 is compressed.

[0037] The orifice passage 121 is formed by a groove provided on the inner surface 122 of the valve member 115. The orifice passage 121 extends radially in the cylinder 101 from each end face 116 of the valve member 115, beyond the seat portion 114, toward the center of the valve member 115. The groove constituting the orifice passage 121 has a constant depth from the inner surface 122 of the valve member 115 (the axial length of the piston 102, hereinafter referred to as "axial length"), but a slope may be provided at the bottom of the groove. In addition, the orifice passage 121 is formed as an isosceles triangle with its base provided on the end face 116 in a plan view (see Figure 6).

[0038] The orifice passage 121 has a smaller flow area (orifice area) in the portion that opens to the inside of the seat portion 114 than in the portion that opens to the outside of the seat portion 114. Furthermore, the flow area of ​​the orifice passage 121 expands radially from the radially inside of the cylinder 102 (towards the center of the valve member 115) to the radially outside. In other words, the flow area of ​​the orifice passage 121 is larger when the hydraulic fluid moves in the direction in which it flows into the damper chamber 105 (second direction) than when the hydraulic fluid moves in the direction in which it is discharged from the damper chamber 105 (first direction).

[0039] In the first embodiment, the orifice area of ​​the orifice passage 121, that is, the flow area of ​​the portion of the orifice passage 121 that opens to the inside of the seat portion 114, is the area of ​​the portion of the orifice passage 121 that is inside the seat portion 114 in a plan view (see Figure 6), or in other words, the area of ​​the portion of the vertex of the isosceles triangle formed by the orifice passage 121 that is inside the seat portion 114.

[0040] When the operating arm 4 rotates counterclockwise from the neutral position (see Figure 2), the piston 102 moves to the right, compressing the damper chamber 105, and the hydraulic fluid from the damper chamber 105 flows to the oil chamber 7 via the multiple orifice passages 121 and connecting passages 112. Here, as the hydraulic fluid from the damper chamber 105 passes through each orifice passage 121, hydraulic resistance acts on the piston 102.

[0041] When the operating arm 4 rotates clockwise and returns to the neutral position (see Figure 2), the piston 102 moves to the left in conjunction with the operating arm 4, and the damper chamber 105 expands. At this time, the valve member 115 separates from the seat portion 114, causing the valve 113 to open and the damper chamber 105 to communicate with the oil chamber 7 via the communication passage 112, so the hydraulic resistance generated on the piston 102 side is negligible.

[0042] In the valve device described in Patent Document 1, a small-diameter hole penetrating the plate-shaped valve member in the thickness direction was used as the orifice passage. As a result, foreign matter could clog the orifice passage, preventing the flow area from being secured, which could increase the hydraulic resistance generated by the oil damper. In this case, a delay would occur in the intake and exhaust of the valve device, increasing the time it would take for the horizontal lever of the valve device to return to the neutral position, and consequently the time it would take for the vehicle height to return to its normal position, potentially reducing the running stability of the railway vehicle.

[0043] Therefore, in the first embodiment, a groove is provided on the inner surface 122 of the valve member 115 that extends radially (hereinafter referred to as "radial direction") across the seat portion 114 to form multiple (four in the first embodiment) orifice passages 121. As a result, even if some (for example, one) orifice passages 121 become clogged with foreign matter, the remaining orifice passages 121 can ensure a flow area (orifice area). According to the first embodiment, the reliability of the valve device 1 is improved, and consequently, the running stability of the railway vehicle can be ensured. Furthermore, in the first embodiment, the flow area inside the seat portion 114 of the orifice passage 121 is made smaller than the flow area outside the seat portion 114. Therefore, even if foreign matter clogs the radially outer opening of the orifice passage 121, the foreign matter can be easily removed when the hydraulic fluid flows from the connecting passage 112 through the valve 113 to the damper chamber 105. In other words, the orifice passage 121 can be automatically cleaned.

[0044] (Second Embodiment) Next, a second embodiment will be described with reference to Figures 4 and 7. Regarding parts common to the first embodiment, the same designations and symbols will be used, and redundant explanations will be omitted.

[0045] In the first embodiment, a groove extending radially across the seat portion 114 was provided on the inner surface 122 of the valve member 115 to form multiple orifice passages 121. In contrast, in the second embodiment, the valve member 161 was divided into a first valve member 162 that abuts against the seat portion 114 and a second valve member 165 provided between the first valve member 162 and the valve spring 119 (biasing member), and the gap in the axial direction (left-right direction in Figure 4, hereinafter referred to as "axial direction") of the cylinder 101 formed between the first valve member 162 and the second valve member was made into an orifice passage (first passage 168).

[0046] Multiple hemispherical protrusions 167 (four in the second embodiment) are provided on the inner surface 166 (the surface facing the first valve member 162) of the second valve member 165. The protrusions 167 are arranged at equal intervals in the circumferential direction on a circle centered on the center of the second valve member 165. By bringing the protrusions 167 into contact with the outer surface 163 of the first valve member 162, a first passage 168 having a constant axial length is formed between the first valve member 161 and the second valve member 165.

[0047] A second passage 164 is provided in the center of the first valve member 162, penetrating the first valve member 162 axially (the "left-right direction" in Figure 4). The second passage 164 is a flow path with a circular cross-section and a constant flow area. The second passage 164 connects the first passage 168 and the connecting passage 112. The axial length of the first passage 168, that is, the height of the projection 167 protruding from the inner surface 166 of the second valve member 165, is set to be smaller than the inner diameter (width) of the flow path of the second passage 164. Also, the circumferential length of the first passage 168 (the distance between adjacent projections 167, 167 in the second embodiment) is set to be larger than the inner diameter (width) of the flow path of the second passage 164.

[0048] When the operating arm 4 rotates counterclockwise from the neutral position (see Figure 2), the piston 102 moves to the right, compressing the damper chamber 105. The hydraulic fluid in the damper chamber 105 then flows through the orifice passages, namely the first passage 168 and the second passage 164, and further through the connecting passage 112 to the oil chamber 7. Here, the hydraulic fluid in the damper chamber 105 passes through the first passage 168, namely the small gap (orifice) between the first valve member 162 and the second valve member 165, causing hydraulic resistance to act on the piston 102.

[0049] Furthermore, when the operating arm 4 rotates clockwise and returns to the neutral position (see Figure 2), the piston 102 moves to the left in conjunction with the operating arm 4, and the damper chamber 105 expands. At this time, 1 Valve member 16 2 As the piston 102 separates from the seat portion 114, the valve 113 opens, and the damper chamber 105 communicates with the oil chamber 7 via the communication passage 112. Therefore, the hydraulic resistance generated on the piston 102 side is negligible.

[0050] In the second embodiment, the valve device includes a first valve member 162 that abuts against the seat portion 114 and a second valve member 165 provided between the first valve member 162 and the valve spring 119 (biasing member). An orifice passage is formed by a first passage 168 (minor gap) provided between the first valve member 162 and the second valve member 165 and a second passage 164 provided in the first valve 162. Therefore, even if foreign matter clogs a part of the peripheral edge of the first passage 168, the flow area can be secured by the other openings. This improves the reliability of the valve device 1 and ensures the running stability of the railway vehicle.

[0051] The second embodiment can be configured as follows. The number of protrusions 167 provided on the second valve member 165 is not intended to be limited to four; it may be three or more. Furthermore, although the projection 167 is positioned on a single circle centered on the center of the second valve member 165, it may also be positioned on concentric circles centered on the center of the second valve member 165. Furthermore, the projection 167 can be in the shape of an arc extending along a circle centered on the center of the second valve member 165.

[0052] (Third embodiment) Next, a third embodiment will be described with reference to Figures 5 and 8. Regarding parts common to the second embodiment, the same designations and symbols will be used, and redundant explanations will be omitted.

[0053] In the second embodiment, a first passage 168 (orifice passage) is formed between the first valve member 162 and the second valve member 165 by providing a plurality of protrusions 167 on the inner surface 166 of the second valve member 165. In contrast, in the third embodiment, a plurality of first passages 171 (orifice passages) are formed between the first valve member 162 and the second valve member 165 by forming a plurality of grooves (eight in the third embodiment) on the inner surface 166 of the second valve member 165 that extend radially from the center of the second valve member 165 in the direction of the cylinder 101.

[0054] The first passage 171 has a rectangular cross-section and extends radially from the center of the second valve member 165. The inner ends of the first passage 171 converge (communicate) at the center of the second valve member 165, and the outer ends open to each end face 169 and each sliding surface 170 of the second valve member 165. The axial length of the first passage 171, i.e., the depth of the groove with a rectangular cross-section, is set to be greater than the inner diameter (width) of the flow path of the second passage 164. Also, the circumferential length of the first passage 171 (the width of the groove with a rectangular cross-section in the third embodiment) is set to be less than the inner diameter (width) of the flow path of the second passage 164.

[0055] In the third embodiment, the same effects and advantages as those of the first and second embodiments described above are achieved. That is, even if a foreign object clogs a part of the first passage 171, the flow area can be secured by the other first passages 171. In the third embodiment, the axial length of the first passage 171 may be set to be smaller than the inner diameter (width) of the second passage 164, and the circumferential length of the first passage 171 may also be set to be smaller than the inner diameter (width) of the second passage 164.

[0056] Furthermore, the present invention is not limited to the embodiments described above, and various modifications are included. For example, the embodiments described above are described in detail to make the present invention easier to understand, and are not necessarily limited to those having all the configurations described. Also, it is possible to replace a part of the configuration of one embodiment with the configuration of another embodiment, and it is also possible to add the configuration of another embodiment to the configuration of one embodiment. In addition, it is possible to add, delete, or replace parts of the configuration of each embodiment with other configurations.

[0057] This application claims priority under Japanese Patent Application No. 2022-042634, filed on 17 March 2022. The entire disclosure of Japanese Patent Application No. 2022-042634, filed on 17 March 2022, including the specification, claims, drawings, and abstract, is incorporated into this application by reference. [Explanation of Symbols]

[0058] 1 Valve device, 2 Housing, 7 Oil chamber, 12 Compressor (fluid source), 13 Air spring (fluid-operated equipment), 101 Cylinder, 102 Piston, 105 Damper chamber, 112 Connecting passage, 113 Valve, 114 Seat section, 115 Valve component, 119 Valve spring (biasing component), 121 Orifice passage

Claims

1. A valve device provided between a fluid source or external source and a fluid-operated device, which controls the supply and discharge of fluid to the fluid-operated device, A housing in which an oil chamber is formed, A cylinder provided in the oil chamber, A piston is provided in the cylinder and defines a damper chamber, A connecting passage is provided in the piston, which connects the damper chamber and the oil chamber, The piston is provided with a valve that controls the flow of the working fluid through the communication passage, The aforementioned valve is The annular seat portion is provided protruding from the piston, and the communication passage opens inside the annular seat portion, A valve member that can be seated and detached from the seat portion, A biasing member that biases the valve member in the closing direction, It has an orifice passage that restricts the flow path of the working fluid between the damper chamber and the communication passage, The orifice passage is formed such that the flow area inside the sheet portion is smaller than the flow area outside the sheet portion. The valve member comprises a first valve member that abuts against the seat portion and a second valve member positioned between the first valve member and the biasing member. The valve device is characterized in that the orifice passage has a plurality of first passages formed between the first valve member and the second valve member, and a second passage provided in the first valve member that connects the plurality of first passages and the connecting passage.

2. A valve device according to claim 1, It has a plurality of protrusions arranged such that a gap is formed between the first valve member and the second valve member, The first passage is formed between adjacent protrusions among the plurality of protrusions, The axial length of the first passage is smaller than the width of the second passage. A valve device characterized in that the circumferential length of the first passage is greater than the width of the second passage.

3. A valve device according to claim 1, The axial length of the first passage is greater than the width of the second passage. A valve device characterized in that the circumferential length of the first passage is smaller than the width of the second passage.

4. A valve device according to claim 3, The axial length of the first passage is smaller than the width of the second passage. A valve device characterized in that the circumferential length of the first passage is smaller than the width of the second passage.

Images