JP6212406B2 - Leveling valve - Google Patents

Description

  The present invention relates to a leveling valve that adjusts the height of an air spring provided in a railway vehicle.

  Patent Document 1 discloses a railway vehicle that includes a lever that rotates according to the relative displacement of the vehicle body with respect to the carriage, and a leveling valve that includes an air supply valve and an exhaust valve that are selectively opened and closed by the rotation of the lever. Has been.

  In the above leveling valve, when the vehicle body is at a predetermined height with respect to the carriage, the lever is in the neutral position, both the air supply valve and the exhaust valve are closed, and the air spring is connected to the compressor and the exhaust port. Is blocked. When the load of the vehicle body increases and the vehicle body sinks with respect to the carriage, the air supply valve opens according to the rotation of the lever, the compressed air is supplied from the compressor to the air spring, and the vehicle body rises. On the other hand, when the load on the vehicle body decreases and the vehicle body rises from the carriage, the exhaust valve opens according to the rotation of the lever, and the compressed air of the air spring is discharged from the exhaust port into the atmosphere, causing the vehicle body to descend. .

  In this type of leveling valve, a check valve is interposed in a supply passage for supplying compressed air to the air spring via the air supply valve.

  The check valve includes a valve body that sits on an annular seat portion to open and close the supply passage, a spring that presses the valve body against the seat portion, and a guide body that slidably supports the valve body on a support wall. .

  The check valve is closed when compressed air is led to the air spring via the air supply valve, and is opened when the air in the air spring is led to the compressor side. In the leveling valve, the check valve is closed to prevent the air from the air spring from flowing back to the compressor side.

JP 2007-76480 A

  However, in such a conventional leveling valve, the check valve is frequently opened and closed as the air spring is frequently supplied and discharged during operation of the railway vehicle. For this reason, the guide body that slides on the support wall is worn, and there is a problem that it is difficult to ensure the durability of the check valve.

  In addition, since the leveling valve has a limited space in which the check valve is interposed, an attempt to increase the thickness of the guide body to ensure the durability of the check valve reduces the thickness of the valve body. Therefore, there arises a problem that the sealing performance of the check valve cannot be secured.

  This invention is made | formed in view of said problem, and it aims at providing the leveling valve which can ensure the durability and sealing performance of a non-return valve.

  The present invention relates to a leveling valve that adjusts the height of an air spring provided between a vehicle body and a carriage of a railway vehicle, the supply passage for guiding compressed air from a compressed air source to the air spring, and the supply passage. A check valve that allows only the flow of compressed air that is guided from the compressed air source to the air spring, and a receiving hole that receives the check valve, and the check valve is seated on the annular seat portion. A valve body that opens and closes the supply passage, a biasing member that presses the valve body against the seat portion, and a guide body that is interposed between the valve body and the biasing member and is slidably supported by the support wall of the accommodation hole The guide body includes a guide portion that slides along the support wall, and a retainer portion that extends in a radial direction from the guide portion and engages with the valve body, and the guide body has a radial direction. Is characterized in that it is thicker than the axial thickness of the retainer portion.

  In the present invention, since the radial thickness of the guide portion is thicker than the axial thickness of the retainer portion, the guide body ensures the radial thickness of the guide portion that slides along the support wall. it can. Further, since the axial thickness of the retainer portion is thinner than the radial thickness of the guide portion, the axial thickness of the valve element can be secured. Thereby, durability and sealing performance of the check valve can be ensured while suppressing an increase in size of the guide body.

It is an attachment figure of the leveling valve concerning a 1st embodiment of the present invention. It is a block diagram of a leveling valve. It is sectional drawing of a non-return valve. It is sectional drawing which shows a part of check valve. It is a top view which shows a part of check valve. It is sectional drawing which shows a part of check valve which concerns on 2nd Embodiment of this invention.

  Hereinafter, embodiments of the present invention will be described with reference to the accompanying drawings.

(First embodiment)
First, the outline of the leveling valve 100 will be described with reference to FIG.

  An air spring 3 is provided between the vehicle body 1 and the carriage 2 of the railway vehicle. The leveling valve 100 supplies and discharges compressed air to and from the air spring 3, and has a function of maintaining the vehicle body 1 at a constant height.

  The leveling valve 100 is attached to the vehicle body 1. The lever 4 of the leveling valve 100 is connected to the carriage 2 via a connecting rod 5. When the air spring 3 expands and contracts due to the load change of the vehicle body 1 and the height of the vehicle body 1 changes, the lever 4 rotates via the connecting rod 5 and the leveling valve 100 operates as follows.

  When the vehicle body 1 is at a predetermined height with respect to the carriage 2, the lever 4 is in the neutral position. In the leveling valve 100, the supply valve 31 (see FIG. 2) and the exhaust valve 32 (see FIG. 2) Both close. Thus, the air spring passage 6 communicating with the air spring 3 is blocked from the air source passage 9 communicating with the compressor 7 (compressed air source) and the exhaust port 8A, and the air spring 3 is maintained at a constant height.

  When the vehicle body load increases and the air spring 3 bends, the lever 4 is pushed upward from the neutral position to rotate in the direction of arrow A in FIG. 1, and accordingly the air supply valve 31 of the leveling valve 100. (See FIG. 2) opens. Thereby, the air spring passage 6 and the compressor 7 communicate with each other, and compressed air from the compressor 7 is supplied to the air spring 3 through a supply passage 10 described later. When the air spring 3 is restored to a certain height, the lever 4 returns to the neutral position, the air supply valve 31 of the leveling valve 100 is closed, and the supply of compressed air is shut off.

  On the other hand, when the vehicle body load decreases and the air spring 3 extends, the lever 4 is pulled downward from the neutral position and rotates in the direction of arrow B in FIG. 1, and accordingly, the exhaust valve 32 of the leveling valve 100. (See FIG. 2) opens. Thereby, the air spring passage 6 and the exhaust passage 8 (see FIG. 2) communicate with each other, and the compressed air of the air spring 3 is discharged from the exhaust port 8A to the atmosphere. When the air spring 3 is restored to a certain height, the lever 4 returns to the neutral position, the exhaust valve 32 of the leveling valve 100 is closed, and the discharge of compressed air is blocked.

  Thus, the leveling valve 100 automatically adjusts the relative displacement generated between the vehicle body 1 and the carriage 2 to maintain the height of the vehicle body 1 constant.

  Next, the leveling valve 100 will be described in detail mainly with reference to FIG.

  The leveling valve 100 includes a buffer spring portion 20 disposed in the center, an air supply valve 31 and an exhaust valve 32 disposed in the upper portion, a damper 25 disposed in the lower portion, and a valve housing 11 that accommodates them. Is provided.

  The buffer spring portion 20 includes a swing arm (not shown) fixed to the support shaft 21, an operation arm 22 that is rotatable with respect to the support shaft 21, and a swing arm and the operation arm 22 wound around the support shaft 21. And a buffer spring 23 to be urged. The rotation of the lever 4 is transmitted to the operating arm 22 through the swing arm and the buffer spring 23. That is, the operating arm 22 rotates as the lever 4 rotates.

  The air supply valve 31 and the exhaust valve 32 are arranged symmetrically around the operation arm 22 in the neutral position, and have a gap between the operation arm 22. Thereby, the supply valve 31 and the exhaust valve 32 are not opened with respect to the rotation of the operation arm 22 less than a predetermined angle, and hunting is prevented.

  The damper 25 includes a piston (not shown) that is connected to the base end side of the operating arm 22 and moves as the operating arm 22 rotates. The piston is soaked in an oil chamber 15 formed in the valve housing 11, and when the operating arm 22 rotates from the neutral position, it provides resistance to the rotating operation of the operating arm 22 while operating. When the arm 22 returns to the neutral position, little resistance is applied to the operating arm 22.

  The leveling valve 100 includes a supply passage 10 that guides compressed air that has passed through the air supply valve 31, and a check valve 40 that is interposed in the supply passage 10 and that allows only the flow of compressed air that is guided from the compressor 7 to the air spring 3. And comprising. Thereby, the air from the air spring 3 is prevented from flowing back to the compressor 7 side via the supply passage 10.

  Next, a specific configuration of the check valve 40 will be described with reference to FIG. In the figure, O is the center line of the check valve 40. The “axial direction” described later means a direction in which the center line O extends, and the “radial direction” means a radial direction centered on the center line O.

  The check valve 40 is accommodated in the accommodation hole 12 of the valve housing 11. The accommodation hole 12 is connected at its lower end to the outlet 16 of the air supply valve 31, and is connected at its upper end to a through hole (not shown) communicating with the air spring 3. The upper opening end of the accommodation hole 12 is closed by a cap 70 via a packing 75. The cap 70 is attached by being screwed to the inner peripheral screw portion 14 of the accommodation hole 12. The open end of the through hole 17 that defines the outlet 16 is closed by a plug 48. The housing hole 12 defines a supply passage 10 that guides compressed air from the compressor 7 to the air spring 3.

  The accommodation hole 12 is formed in a cylindrical surface shape centered on the center line O, and a valve seat 45 is interposed at the lower end of the accommodation hole 12. The valve seat 45 has a seat portion 46 that protrudes in an annular shape around the center line O.

  The check valve 40 is interposed between a valve body 61 seated on the seat portion 46, a coil spring 47 (biasing member) that presses the valve body 61 against the seat portion 46, and the valve body 61 and the coil spring 47. And a metal guide body 51 that is slidably supported by the support wall 13 located at the center of the accommodation hole 12.

  Between the valve seat 45 and the cap 70, a valve body 61, a guide body 51, and a coil spring 47 are arranged side by side in the axial direction. The coil spring 47 is interposed between the cap 70 and the guide body 51 by being compressed.

  In the check valve 40, the guide body 51 closes when the valve body 61 is seated on the seat portion 46 by the biasing force of the coil spring 47, while the valve body 61 resists the biasing force of the coil spring 47. The valve is opened by leaving 46. When the check valve 40 is opened and closed, the guide body 51 slides on the support wall 13 so that the valve body 61 is guided so as not to be inclined with respect to the center line O.

  As shown in FIGS. 4 and 5, the metal guide body 51 includes a disk-shaped retainer portion 52 extending in the radial direction and a guide portion 54 bent from the retainer portion 52 and extending in the axial direction.

  The retainer portion 52 is formed in a flat plate shape having a constant axial thickness T1. The thickness of the retainer portion may not be constant, but the workability is better if it is constant.

  The radial thickness T2 of the guide portion 54 on the retainer portion 52 side (base end portion) is formed so as to be thicker than the axial thickness T1 of the retainer portion 52.

  Further, the inner peripheral surface of the guide portion 54 is formed in a tapered shape whose inner diameter gradually expands from the retainer portion 52 side (base end portion) to the seat portion 46 side (tip end portion), and the outer peripheral surface of the guide portion 54 is In addition, it is formed parallel to the center line O so as to slide on the support wall 13. That is, the radial thickness T2 of the guide portion 54 is formed so as to gradually become thinner from the proximal end portion to the distal end portion.

  The valve body 61 is formed of an elastic material such as rubber. The valve body 61 includes a truncated cone-shaped valve body portion 62 seated on the seat portion 46, a columnar valve body-side spring guide portion 63 that guides the coil spring 47, a valve body portion 62, and a valve body-side spring guide portion 63. And an annular groove 64 opened between the two. The valve body 61 is connected to the guide body 51 by engaging the annular groove 64 with the retainer portion 52.

  The valve body portion 62 is formed on the base portion surface 62A that contacts the retainer portion 52, the valve body portion outer peripheral surface 62B (outer peripheral surface) that faces the inner peripheral surface of the guide portion 54, and the seat portion 46 side. It is formed in a truncated cone shape having a tip surface 62C parallel to the end surface 62A. A gap is provided between the inner peripheral surface of the guide portion 54 and the valve body outer peripheral surface 62B. Thereby, the amount of collapse of the valve body 62 when the valve body 62 abuts against the seat portion 46 can be allowed.

  The outer diameter D2 of the base end face 62A is formed larger than the diameter D1 of the seating part 62D (contact part) seated on the seat part 46 on the front end face 62C. That is, the base end face 62A is arranged on the axial extension of the seat part 46 of the valve body 61 without the valve body outer peripheral surface 62B being arranged. As a result, the valve body portion 62 has a thickness T3 in the axial direction of the portion that contacts the seat portion 46. That is, a sufficient collapse allowance for the valve body 62 can be secured, and the sealing performance of the check valve 40 can be secured.

  A plurality of guide portions 54 (here, four) are formed, and an arcuate cutout portion 57 is formed between the guide portions 54. The notch 57 forms a flow path through which compressed air flows when the valve is opened.

  As shown in FIG. 3, the upper end portion of the coil spring 47 is guided by the cap-side spring guide portion 71 of the cap 70 and abuts on the stepped portion 72 of the cap 70. The lower end portion of the coil spring 47 is guided by the valve body side spring guide portion 63 of the valve body 61 and comes into contact with the retainer portion 52. Thereby, the coil spring 47 can expand and contract in the axial direction around the center line O.

  Next, the operation of the check valve 40 will be described.

  The check valve 40 is closed when the air in the air spring 3 is guided to the compressor 7 side. In the leveling valve 100, the check valve 40 blocks the supply passage 10, thereby preventing the air from the air spring 3 from flowing backward to the compressor 7 side.

  When the check valve 40 is closed, the front end surface 62C of the valve body portion 62 is pressed against the seat portion 46 by the urging force of the coil spring 47 and the air discharged from the air spring 3, and the seat portion 62D is seated. Sit on. At this time, since the axial thickness T3 of the valve body 62 is sufficiently ensured as described above, the seating portion 62D contacts the seat portion 46 without a gap.

  The check valve 40 opens when the compressed air from the compressor 7 is guided through the air supply valve 31. When the valve is opened, the valve body 61 moves against the urging force of the coil spring 47, and the valve body portion 62 is separated from the seat portion 46. When the seat portion 46 is thus opened, the compressed air that has passed through the seat portion 46 flows between the notch portion 57 and the support wall 13 and around the valve body 61. That is, the compressed air from the compressor 7 is supplied to the air spring 3 through the supply passage 10.

  In the leveling valve 100, the check valve 40 is frequently opened and closed as air is frequently supplied to the air spring 3 during operation of the railway vehicle. Therefore, the guide portion 54 of the guide body 51 that slides on the support wall 13 is worn, and it is difficult to ensure durability.

  In the guide portion 54, the radial thickness T2 on the retainer portion 52 side (base end portion) of the guide portion 54 is thicker than the axial thickness T1 of the retainer portion 52, and from the base end portion to the tip end portion. Since the thickness is gradually reduced, the durability and sealing performance of the check valve 40 can be ensured.

  According to the above 1st Embodiment, there exists an effect shown below.

  [1] The leveling valve 100 is provided in the supply passage 10 that guides the compressed air from the compressor 7 (compressed air source) to the air spring 3 and the flow of the compressed air that is provided in the supply passage 10 and that is guided from the compressor 7 to the air spring 3. A check valve 40 that allows only the check valve 40 and a housing hole 12 that houses the check valve 40. The check valve 40 is seated on an annular seat portion 46 to open and close the supply passage 10, a coil spring 47 (biasing member) that presses the valve body 61 against the seat portion 46, the valve body 61 and the coil A guide body 51 interposed between the spring 47 and slidably supported by the support wall 13 of the accommodation hole 12. The guide body 51 includes a guide portion 54 that slides along the support wall 13, and a retainer portion 52 that extends in the radial direction from the guide portion 54 and engages with the valve body 61. The radial thickness T2 of the guide portion 54 is thicker than the axial thickness T1 of the retainer portion 52.

  Based on the above configuration, the guide body 51 is formed so that the radial thickness T2 of the guide portion 54 is thicker than the axial thickness T1 of the retainer portion 52. A thickness T2 of the sliding guide portion 54 can be secured, and durability is improved. Further, since the axial thickness T1 of the retainer portion 52 is formed thinner than the radial thickness T2 of the guide portion 54, the axial thickness T3 of the valve body 61 is suppressed while suppressing an increase in the size of the guide body 51. Can be secured, and the collapse allowance of the valve body 61 can be sufficiently secured, so that the valve body 61 can abut against the seat portion 46 without a gap. Thereby, in the leveling valve 100, durability and sealing performance of the check valve 40 can be ensured.

  The check valve 40 does not need to change the size of the receiving hole 12 in the valve housing 11 by avoiding an increase in the size of the guide body 51. As a result, the check valve 40 can be used as a replacement part for the current leveling valve.

  [2] In the valve body 61, an annular groove 64 with which the retainer portion 52 engages, and a valve body outer peripheral surface 62B (outer peripheral surface) of the valve body 61 is formed from the annular groove 64 along the inner peripheral surface of the guide portion 54. And a valve body portion 62 to be configured.

  Based on the above configuration, the valve body 62 contacts the retainer 52 and the guide 54 when the valve is closed, so that the valve body 61 is moved to the seat 46 by the urging force of the coil spring 47 and the air discharged from the air spring 3. Since it can be surely pressed, the valve body 61 comes into contact with the seat portion 46 without a gap. Thereby, the sealing performance of the check valve 40 can be ensured.

  [3] The radial thickness T2 of the guide portion 54 is formed so that the thickness gradually decreases from the proximal end portion on the retainer portion 52 side to the distal end portion on the seat portion 46 side.

  Based on the above configuration, the guide body 51 is formed such that the thickness T2 of the proximal end portion of the guide portion 54 is thick. That is, the thickness of the bent portion between the retainer portion 52 and the guide portion 54 can be secured, and the durability of the check valve 40 can be secured. Further, since the valve body portion outer peripheral surface 62B of the valve body portion 62 is formed along the inner peripheral surface of the guide portion 54, the thickness of the valve body portion 62 on the seat portion 46 side can be secured. Thereby, the valve body part 62 contacts the seat part 46 without a gap, and the sealing performance of the check valve 40 can be secured.

  [4] The valve body 61 includes a base end surface 62A that contacts the retainer portion 52 and a valve body portion 62 in which a front end surface 62C on the seat portion 46 side is formed. The distal end surface 62C further includes a seating portion 62D (contact portion) seated on the seat portion 46, and the outer diameter D2 of the base end surface 62A is formed to be larger than the diameter D1 of the seating portion 62D. .

  Based on the above configuration, since the base end face 62A is disposed on the axial extension of the seat portion 46 of the valve body portion 62, the axial thickness T3 of the portion that contacts the seat portion 46 of the valve body portion 62 is determined. It is ensured and the collapse allowance of the valve body 62 can be sufficiently secured. As a result, the seating part 62D abuts against the seat part 46 without any gap, and the sealing performance of the check valve 40 can be ensured.

(Second Embodiment)
Next, a second embodiment of the present invention will be described with reference to FIG. Below, it demonstrates centering on a different point from the said 1st Embodiment, the same code | symbol is attached | subjected to the structure same as the leveling valve 100 of the said 1st Embodiment, and description is abbreviate | omitted.

  In the check valve 40 of the leveling valve 100 according to the first embodiment, the inner diameter of the inner peripheral surface of the guide portion 54 of the guide body 51 is tapered. On the other hand, in the check valve 140 of the leveling valve according to the second embodiment, the inner diameter of the inner peripheral surface of the guide portion 154 of the guide body 151 is formed to be the same diameter.

  The metal guide body 151 includes a disk-shaped retainer portion 152 extending in the radial direction and a plurality (four in this case) of guide portions 154 bent from the retainer portion 152 and extending in the axial direction. An arcuate cutout (not shown) is formed between the guide portions 154.

  The retainer part 152 is formed in a flat plate shape having a constant axial thickness T4.

  The guide portion 154 is formed in a uniform straight shape with a radial thickness T5 from the retainer portion 152 side (base end portion) to the seat portion 46 (tip end portion). An inner peripheral surface of the guide portion 154 faces an outer periphery of a valve body 161 described later, and the outer peripheral surface of the guide portion 154 slides along the support wall 13. The inner peripheral surface and the outer peripheral surface of the guide portion 154 are formed in parallel to the center line O. Thereby, the workability of the guide body 151 is improved.

  The thickness T5 in the radial direction of the guide portion 154 is formed so as to be thicker than the thickness T4 in the axial direction of the retainer portion 152.

  The valve body 161 includes a columnar valve body portion 162 seated on the seat portion 46, a columnar valve body side spring guide portion 163 that guides the coil spring 47, and the valve body portion 162 and the valve body side spring guide portion 163. And an annular groove 164 opening therebetween. The valve body 161 is connected to the guide body 151 by engaging the annular groove 164 with the retainer portion 152.

  The valve body portion 162 is formed on the base end surface 162A that contacts the retainer portion 152, the valve body portion outer peripheral surface 162B (outer peripheral surface) formed along the inner peripheral surface of the guide portion 154, and the seat portion 46 side. And a tip surface 162C. The distal end surface 162C has a seating surface 162D (contact portion) that is inclined from the center line O toward the outer peripheral direction. Thereby, even when the valve body 161 is tilted, the seating surface 162D can be in contact with the seat portion 46 without a gap.

  A gap is provided between the inner peripheral surface of the guide portion 154 and the valve body outer peripheral surface 162B. As a result, the amount of collapse of the valve body 162 when the valve body 162 abuts against the seat portion 46 can be allowed.

  The outer diameter D4 of the base end surface 162A is formed larger than the diameter D3 of the seating surface 162D seated on the seat portion 46. That is, the base end surface 162A is disposed on the extension of the seat portion 46 in the axial direction without the valve body outer peripheral surface 162B being disposed. Thereby, the axial thickness of the site | part contact | abutted to the sheet | seat part 46 is ensured. That is, the collapse allowance of the valve body 162 can be sufficiently secured, and the sealing performance of the check valve 40 can be secured.

  Since the guide portion 154 has a thickness T5 in the radial direction that is thicker than the thickness T4 in the axial direction of the retainer portion 152, the durability and sealing performance of the check valve 140 can be ensured.

  According to the above 2nd Embodiment, while exhibiting the effect of said [1] similarly to 1st Embodiment, there exists the effect shown below.

  [5] The valve body 161 has an annular groove 164 with which the retainer portion 152 is engaged, and a valve body in which a valve body outer peripheral surface 162B (outer peripheral surface) is formed from the annular groove 164 along the inner peripheral surface of the guide portion 154. Part 162.

  Based on the above configuration, the valve body 162 abuts against the retainer 152 and the guide part 154 when the valve is closed, so that the valve body 161 is moved to the seat 46 by the urging force of the coil spring 47 and the air discharged from the air spring 3. Since it can be surely pressed, the valve body 161 abuts against the seat portion 46 without a gap. Thereby, the sealing performance of the check valve 140 can be ensured.

  [6] The valve body 161 has a valve body portion 162 having a distal end surface 162C formed on the seat portion 46 side. The distal end surface 162C is configured to have a tapered shape that is inclined from the center of the valve body 161 to the outer periphery.

  Based on the above configuration, the front end surface 162C is formed in a tapered shape that inclines from the center of the valve body 161 to the outer periphery, so that the front end surface 162C abuts against the seat portion 46 even when the valve body 161 is inclined. Can do. Thereby, the sealing performance of the check valve 140 can be ensured.

  [7] The valve body 161 includes a base end surface 162A that contacts the retainer portion 152 and a valve body portion 162 having a distal end surface 162C formed on the seat portion 46 side. The distal end surface 162C further includes a seating surface 162D (contact portion) that sits on the seat portion 46, and the outer diameter D4 of the base end surface 162A is formed larger than the diameter D3 of the seating surface 162D. .

  Based on the above configuration, the base end surface 162A is disposed on the axial extension of the seat portion 46 of the valve body portion 162, so that the thickness of the portion that contacts the seat portion 46 is secured, and the valve body portion 162 is crushed. You can secure enough bills. As a result, the seating surface 162 </ b> D contacts the seat portion 46 without a gap, and the sealing performance of the check valve 140 can be ensured.

  The embodiment of the present invention has been described above. However, the above embodiment only shows a part of application examples of the present invention, and the technical scope of the present invention is limited to the specific configuration of the above embodiment. Absent.

  For example, in the said embodiment, although the guide bodies 51 and 151 have the four guide parts 54 and 154, it is not restricted to this, A guide body has 1-3 or 5 or more guide parts. It may be.

  Moreover, although a notch part is formed between each guide part, since the flow path through which compressed air flows at the time of valve opening should just be formed, a through-hole may be sufficient, for example.

DESCRIPTION OF SYMBOLS 1 Bogie 2 Car body 3 Air spring 10 Supply passage 12 Housing hole 13 Support wall 40,140 Check valve 46 Seat part 47 Coil spring (biasing member)
51, 151 Guide body 52, 152 Retainer part 54, 154 Guide part 61, 161 Valve body 62, 162 Valve body part 62A, 162A Base end face 62B, 162B Valve body side outer peripheral surface (outer peripheral surface)
62C, 162C Front end surface 62D Seating part (contact part)
162D Seating surface (contact part)
64, 164 annular groove 100 leveling valve

Claims (5)

A leveling valve that adjusts the height of an air spring provided between a body of a railway vehicle and a carriage,
A supply passage for guiding compressed air from a compressed air source to the air spring;
A check valve provided in the supply passage and allowing only a flow of compressed air guided from the compressed air source to the air spring;
An accommodation hole for accommodating the check valve,
The check valve is
A valve body that sits on an annular seat and opens and closes the supply passage;
A biasing member that presses the valve body against the seat portion;
A guide body interposed between the valve body and the biasing member and slidably supported by a support wall of the accommodation hole,
The guide body includes a guide portion that slides along the support wall;
A retainer portion extending in a radial direction from the guide portion and engaged with the valve body,
The leveling valve according to claim 1, wherein a thickness of the guide portion in a radial direction is thicker than a thickness of the retainer portion in an axial direction. The valve body is
An annular groove with which the retainer part engages;
The leveling valve according to claim 1, further comprising: a valve body portion having an outer peripheral surface formed along the inner peripheral surface of the guide portion from the annular groove.   The thickness in the radial direction of the guide portion is formed so that the thickness gradually decreases from a proximal end portion on the retainer portion side to a distal end portion on the seat portion side. The leveling valve described. The valve body has a valve body portion having a tip surface formed on the seat portion side,
The leveling valve according to any one of claims 1 to 3, wherein the tip surface is formed in a tapered shape inclined from the center of the valve body to the outer periphery. The valve body is
A base end surface that contacts the retainer portion;
A valve body portion having a tip surface formed on the seat portion side,
The front end surface further has a contact portion seated on the seat portion,
The leveling valve according to any one of claims 1 to 4, wherein an outer diameter of the base end surface is formed larger than a diameter of the contact portion.

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