TW201827725A - Leveling valve - Google Patents

Abstract

A leveling valve (100) according to the present invention comprises: a piston (20) that is accommodated in an accommodation hole (11a) formed in a housing (10) and moves inside the accommodation hole (11a) in accordance with the amount of relative displacement of a vehicle body (1) with respect to a dolly (2); and a rotation restricting portion (50) that is provided on the housing (10) and the piston (20) and restricts the piston (20) from rotating about a first central axis (O1) of the accommodation hole (11a) while guiding the piston (20) along a direction of the first central axis (O1).

Description

 Horizontal valve  

The present invention is directed to a horizontal valve.

A horizontal valve is described in JP2004-52889A, which supplies a compressed air to an air spring provided between a vehicle body and a trolley of a railway vehicle or the like, or discharges compressed air from the air spring, so that the height of the vehicle body is kept constant. .

In the horizontal valve described in JP2004-52889A, if the support height of the vehicle body realized by the air spring changes due to the load change of the vehicle body, the rotor rotates corresponding to the amount of change, and the swirling motion of the rotor passes through the pin. It is converted into a reciprocating motion of the piston along the axial direction. In the air spring passage connected to the air spring, a supply passage connected to the air pressure supply source and an exhaust passage opening to the atmosphere are selectively connected corresponding to a moving direction of the piston, that is, a direction in which the height of the vehicle body changes. Either.

Further, a flat portion orthogonal to the rotational axis of the rotor is formed on the outer circumference of the piston of the horizontal valve. By the planar portion being in contact with the end surface of the rotor, the piston can be moved in the axial direction without being rotated about the central axis.

However, in the horizontal valve described in JP2004-52889A, since the rotating shaft of the rotor is in an orthogonal relationship with the moving central axis of the piston, in order to smoothly rotate the rotor, it is necessary to face the plane of the piston and the end of the rotor. Set a gap between specific sizes. Further, if the size of the gap is increased by the assembly error or the wear of the rotor sliding portion, the piston and the rotor are not in surface contact, but are in partial contact, and the piston and the rotor are in a state of being easily partially worn.

If the distance between the piston and the rotor is further enlarged by the wear of the piston and the rotor, and the piston is unable to contact the rotor, the piston will rotate about the central axis. If the piston rotates in this way, the displacement of the rotor cannot be normally transmitted to the piston, and the operation of the horizontal valve becomes unstable, so that it is difficult to keep the height of the vehicle body fixed.

It is an object of the invention to operate the horizontal valve stably.

According to a certain aspect of the present invention, the horizontal valve adjusts the height of the air spring disposed between the vehicle body and the trolley of the vehicle, and includes: a housing formed with an air spring passage communicating with the air spring; and a piston; The slidably accommodated in the receiving hole formed in the casing and moves in the receiving hole corresponding to the relative displacement of the vehicle body with respect to the trolley; and the rotation restricting portion provided in the casing and The piston guides the piston along a central axis direction of the accommodation hole, and restricts rotation of the piston around the central axis.

1‧‧‧ body

2‧‧‧Trolley

3‧‧‧Air spring

4‧‧‧ rod

4a‧‧‧ fitting holes

5‧‧‧Connecting rod

6‧‧‧Air spring passage

7‧‧‧Compressor

8‧‧‧ exhaust passage

9‧‧‧Supply access

10‧‧‧shell

11‧‧‧Main box

11a‧‧‧ receiving hole

11b‧‧‧ openings

11c, 11d, 11e, 12c, 13a, 41h, 48b‧‧‧ pathway

11f‧‧‧Female thread

11g‧‧‧ receiving trough

12‧‧‧1st cover member

12a, 33‧‧‧Flange

12b‧‧‧Insert Department

12d‧‧‧ bottom

12e, 41n‧‧‧ radial prescription

12f‧‧‧Circular direction

13‧‧‧2nd cover member

13b, 20a, 41k, 42e‧‧‧through holes

14‧‧‧ Cover member

14a‧‧‧Connected holes

14b, 41p‧‧‧ support holes

15‧‧‧ accommodating space

16‧‧‧Filter

17, 18 ‧ ‧ bearings

20‧‧‧Piston

21‧‧‧ Guide slot

22‧‧‧ slots

30‧‧‧Rotor

31‧‧‧ Body Department

32‧‧‧Seat

34‧‧‧ Arms

35‧‧ ‧ sales

40‧‧‧Supply discharge valve

41‧‧‧ valve box

41a‧‧‧1st cylindrical part

41b‧‧‧Flange

41c‧‧‧2nd cylindrical part

41d‧‧‧1st insertion hole

41e‧‧‧2nd insertion hole

41f‧‧‧Steps Department

41g‧‧‧1st seat

41i‧‧‧Reducing section

41j‧‧‧Expanding Department

41m‧‧‧ bottom

41r‧‧‧ Tapered

42‧‧‧ valve stem

42a‧‧‧Sliding section

42b‧‧‧Insert Department

42c‧‧‧ end face

42d‧‧‧non-through holes

42f‧‧‧Great Path Department

42g‧‧‧Little Trail Department

43, 44‧‧‧ valve body

45‧‧‧ Spring

46‧‧‧With pad nut

46a‧‧‧The body

48‧‧‧ Plug

48a‧‧‧2nd seat

50, 150, 250‧ ‧ rotation limit

51‧‧‧Restricted board

51a, 53a‧‧‧ first end

51b, 53b‧‧‧2nd end face

51c, 151a, 251a‧‧

51d‧‧‧ outer surface

51e‧‧‧ inner surface

52, 54, 152‧‧ ‧ sliding slots

52a, 54a, 152a, 252a‧‧ ‧ slip joints

53‧‧‧Restrictive bar

53c‧‧‧ outer perimeter

55‧‧‧1st positioning slot

56‧‧‧2nd positioning slot

57‧‧‧ positioning slot

58‧‧‧Positioning holes

100, 200, 300‧‧‧ horizontal valves

151‧‧‧Restricted components

251‧‧‧Restricted tablet

252‧‧‧Sliding

A, B, C, D, E, F‧‧‧ arrows

D1‧‧‧ OD

L1, L2, L3, L4‧‧‧ shortest distance

N‧‧‧Neutral position

O1‧‧‧1st central axis

O2‧‧‧2nd central axis

Fig. 1 is a view showing the mounting of a horizontal valve according to a first embodiment of the present invention.

Fig. 2 is a cross-sectional view showing the horizontal direction of the horizontal valve according to the first embodiment of the present invention.

Figure 3 is a cross-sectional view of the horizontal valve taken along line III-III of Figure 2.

Figure 4 is a cross-sectional view of the horizontal valve taken along line IV-IV of Figure 2.

Figure 5 is a cross-sectional view of the horizontal valve taken along line V-V of Figure 2.

Fig. 6 is a cross-sectional view showing a portion corresponding to Fig. 3 in a modification of the horizontal valve according to the first embodiment of the present invention.

Fig. 7 is a cross-sectional view showing a portion corresponding to Fig. 4 in a modification of the horizontal valve according to the first embodiment of the present invention.

Fig. 8 is a cross-sectional view showing a portion corresponding to Fig. 5 in a modification of the horizontal valve according to the first embodiment of the present invention.

Figure 9 is a cross-sectional view of the horizontal valve taken along line IX-IX of Figure 8.

Fig. 10 is a cross-sectional view showing a portion corresponding to Fig. 3 of a horizontal valve according to a second embodiment of the present invention.

Fig. 11 is a cross-sectional view showing a portion corresponding to Fig. 3 of a horizontal valve according to a third embodiment of the present invention.

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

 <First embodiment>  

An outline of the horizontal valve 100 according to the first embodiment of the present invention will be described with reference to Fig. 1 .

The horizontal valve 100 adjusts the expansion and contraction of the air spring disposed between the body of the railway vehicle and the trolley to maintain the height of the vehicle body relative to the trolley.

As shown in FIG. 1 , the horizontal valve 100 is attached to the vehicle body 1 side, and is coupled to the bogie 2 via the rod 4 and the connecting rod 5 . If the load change of the vehicle body 1 causes the air spring 3 to expand and contract and the height of the vehicle body 1 changes, the change is transmitted to the horizontal valve 100 via the connecting rod 5 and the rod 4.

When the load of the vehicle body increases and the air spring 3 contracts, that is, when the height of the vehicle body 1 relative to the trolley 2 is lower than a predetermined height, the lever 4 is upward from the neutral position shown in FIG. 1 (Fig. 1 arrow A direction) rises. When the rod 4 is displaced upward, the air spring passage 6 communicating with the air spring 3 communicates with the supply passage 9 communicating with the compressor 7 in the horizontal valve 100, wherein the compressor 7 serves as a source of air pressure for supplying compressed air. . Thereby, compressed air is supplied from the compressor 7 to the air spring 3, and the air spring 3 is extended. When the height of the vehicle body 1 with respect to the carriage 2 becomes a predetermined height by the extension of the air spring 3, the lever 4 returns to the neutral position, and the supply of the compressed air to the air spring 3 is stopped.

On the other hand, when the load of the vehicle body is reduced and the air spring 3 is extended, that is, when the height of the vehicle body 1 relative to the trolley 2 is higher than a predetermined height, the lever 4 is lowered downward from the neutral position (Fig. 1). The arrow B direction) is pulled down. When the rod 4 is displaced downward as described above, the air spring passage 6 communicates with the exhaust passage 8 in the horizontal valve 100. Since one end of the exhaust passage 8 is open to the atmosphere, the compressed air in the air spring 3 is discharged to the atmosphere, and the air spring 3 contracts. When the height of the vehicle body 1 with respect to the carriage 2 becomes a predetermined height by the contraction of the air spring 3, the rod 4 returns to the neutral position, and the discharge of the compressed air from the air spring 3 is stopped.

Thus, the horizontal valve 100 selectively communicates the air spring passage 6 to the supply passage 9 or the exhaust passage 8 corresponding to the direction of rotation of the rod 4, wherein the rod 4 is displaced with respect to the carriage 2 relative to the carriage 2 Rotate. Thereby, the relative displacement generated between the vehicle body 1 and the bogie 2 is reduced, and the height of the vehicle body 1 with respect to the bogie 2 is maintained at a predetermined height.

Next, the configuration of the horizontal valve 100 will be described with reference to Figs. 2 to 5 . 2 is a cross-sectional view of the horizontal valve 100, FIG. 3 is a cross-sectional view of the horizontal valve 100 taken along line III-III of FIG. 2, and FIG. 4 is a level along the line IV-IV of FIG. A diagram of a portion of a cross section of the valve 100, and Fig. 5 is a view showing a portion of a section of the horizontal valve 100 along the line VV of Fig. 2.

The horizontal valve 100 includes a casing 10 in which an air spring passage 6, a supply passage 9, and an exhaust passage 8 are formed, a piston 20 slidably housed in the casing 10, and a rotor 30 that faces the vehicle body 1 The relative displacement amount of the bogie 2 is transmitted to the piston 20; and the supply discharge valve 40 is configured to selectively communicate the air spring passage 6 with the supply passage 9 or the exhaust passage 8 in accordance with the moving direction of the piston 20.

The casing 10 has a main casing 11 which is formed with a receiving hole 11a for accommodating the piston 20 along a first central axis O1 on which a central axis is written, and a first cover member 12 attached to one side of the main casing 11. And a second cover member 13 attached to the other side of the main casing 11. The casing 10 is fixed to the vehicle body 1 by attaching the main casing 11 to the vehicle body 1 via a bolt (not shown).

The first cover member 12 has a flange portion 12a that is attached to the main casing 11 via a bolt (not shown), and a cylindrical insertion portion 12b that serves as a first support portion, which is along the flange portion 12a. The center axis O1 extends and is inserted into the receiving hole 11a. The second cover member 13 has a through hole 13b formed to penetrate in the direction of the first central axis O1, and is attached to the main casing 11 via a bolt (not shown) so that the through hole 13b is concentric with the receiving hole 11a.

The main casing 11 and the first cover member 12 are formed with passages 11c, 11d, and 12c constituting the air spring passage 6, respectively. The air spring 3 communicates with the supply and discharge valve 40 via the passages 11c, 11d, and 12c. Further, passages 11e and 13a constituting the supply passage 9 are formed in the main casing 11 and the second cover member 13, respectively. The compressor 7 communicates with the supply and discharge valve 40 via the passages 11e, 13a. Further, the air spring passage 6 may be formed only in the main casing 11 without passing through the first cover member 12. Similarly, the supply passage 9 may be provided only in the second cover member 13 without passing through the main casing 11.

Moreover, as shown in FIG. 3, the main casing 11 is formed with an opening 11b that opens radially outward with respect to the accommodation hole 11a. The casing 10 further has a cover member 14 that covers the opening 11b and is attached to the main casing 11. The accommodating space 15 accommodating the rotor 30 is defined by attaching the cover member 14 to the main casing 11.

The cover member 14 is formed with a communication hole 14a that communicates the accommodation space 15 with the outside. The communication hole 14a functions as an exhaust passage 8 that allows the supply and discharge valve 40 to communicate with the outside. A filter 16 is provided in the communication hole 14a to prevent foreign matter from intruding from the outside.

The supply/discharge valve 40 is composed of a tubular valve case 41 having one end side inserted into the receiving hole 11a of the main casing 11, and the other end side being inserted into the through hole 13b of the second cover member 13, and a valve stem 42. The first central axis O1 extends, and one end side is fixed to the piston 20, the other end side is inserted into the valve casing 41, and the valve bodies 43, 44 are disposed in the valve casing 41. The specific configuration of the supply discharge valve 40 will be described below.

The valve casing 41 has a first cylindrical portion 41a as a second support portion that is inserted into the receiving hole 11a, a second cylindrical portion 41c that is inserted into the second cover member 13, and a flange portion 41b. The outer diameter of the first cylindrical portion 41a and the second cylindrical portion 41c is larger than the outer diameter of the first cylindrical portion 41a and the second cylindrical portion 41c, and a male screw is formed on the outer peripheral surface.

The valve casing 41 is assembled to the main casing 11 by screwing the flange portion 41b to the female screw portion 11f formed in the opening of the accommodation hole 11a. By fixing the second cover member 13 to the main casing 11 so as to cover the second cylindrical portion 41c protruding from the main casing 11, the second cover member 13 restricts the flange portion 41b from coming out of the casing 11. As a result, the case where the valve casing 41 is detached from the casing 11 itself is prevented. Further, the assembly of the valve case 41 with respect to the main casing 11 is not limited to the screwing, and the flange portion 41b can be assembled by fitting the main casing 11 to the main casing 11, and the second cover member 13 can be used. The flange portion 41b is pressed against the main casing 11 to be assembled.

Further, inside the valve casing 41, a first insertion hole 41d is opened in the first cylindrical portion 41a side, and the valve stem 42 is inserted, and the second insertion hole 41e is connected to the first insertion hole 41d. The inner diameter is larger than the inner diameter of the first insertion hole 41d, and the step portion 41f is formed at the connection portion between the first insertion hole 41d and the second insertion hole 41e.

The second insertion hole 41e is opened on the side of the second cylindrical portion 41c, and a cylindrical plug 48 is inserted and fixed to the opening end of the second insertion hole 41e. Thus, the open end of the second insertion hole 41e is closed by the plug 48.

A portion of the inner circumferential portion of the step portion 41f protrudes toward the plug 48 side, and a first valve seat portion 41g having an annular shape centering on the first central axis O1 is formed. Further, the end surface of the plug 48 opposed to the step portion 41f protrudes toward the step portion 41f to form an annular second valve seat portion 48a centering on the first central axis O1. The plug 48 is provided with a passage 48b which is open at the inner peripheral side of the second valve seat portion 48a and has the other end open on the outer peripheral surface of the plug 48.

The second insertion hole 41e is provided with a disk-shaped valve body 43 that is displaced from the first valve seat portion 41g or seated on the first valve seat portion 41g, and a disk-shaped check valve body 44. The second valve seat portion 48a is displaced from or seated on the second valve seat portion 48a, and the spring 45 urges the valve body 43 toward the first valve seat portion 41g, and the check valve body 44 faces the 2 The valve seat portion 48a is pressed. In other words, when the valve body 43 is seated on the first valve seat portion 41g by the pressing force of the spring 45, and the check valve body 44 is seated on the second valve seat portion 48a, the space in the second insertion hole 41e is satisfied. Become closed.

The valve body 43 is slidably supported by the second insertion hole 41e on the outer circumferential surface, and communicates with the space partitioned by the valve body 43 by the notch portions provided in the outer circumferential surface (not shown). Similarly to the valve body 43, the check valve body 44 is connected to a space partitioned by the check valve body 44 by a not-shown portion provided on the outer peripheral surface.

A passage 41h is formed in the valve casing 41, and the passage 41h communicates the passage 13a formed in the second cover member 13 with the passage 48b formed in the plug 48. The compressed air ejected from the compressor 7 passes through the passages 11e, 13a, 41h, 48b and is guided upstream of the check valve body 44.

When the pressure on the upstream side of the check valve body 44, that is, the pressure on the compressor 7 side is higher than the pressure on the downstream side of the check valve body 44, the check valve body 44 resists the urging force of the spring 45 from the second valve seat. The portion 48a is separated to connect the supply passage 9 with the space in the second insertion hole 41e. On the other hand, when the pressure on the compressor 7 side is lower than the pressure on the downstream side of the check valve body 44, the check valve body 44 is seated on the second valve seat portion 48a, thereby feeding the supply passage 9 and the second insertion hole 41e. The connection of the space inside is blocked. In this manner, the check valve body 44 functions as a check valve that allows only the flow toward the valve body 43.

The valve stem 42 is a rod-shaped member and has a sliding portion 42a slidably supported by the valve casing 41, and an insertion portion 42b formed to have an outer diameter smaller than the outer diameter of the sliding portion 42a, and inserted into the piston 20 . The valve stem 42 is fixed to the piston 20 by assembling the pad nut 46 as a coupling member from the end portion of the insertion portion 42b from which the piston 20 protrudes. Specifically, the pad nut 46 has a pad portion 46a having an outer diameter D1 larger than the outer diameter of the insertion portion 42b, and the pad nut 46 is screwed to the end portion of the insertion portion 42b to be the pad portion 46a and The sliding portion 42a sandwiches the state of the piston 20. Further, the coupling member is not limited to the pad nut 46, and may be a combination of a washer and a nut having an outer diameter larger than the outer diameter of the insertion portion 42b, or may be used by being engaged with the insertion portion 42b. A part of the fixing ring or the split pin that protrudes radially from the outer peripheral surface of the insertion portion 42b.

The sliding portion 42a is formed with a non-through hole 42d that is open at the end surface 42c that is inserted into the inside of the valve casing 41, and a plurality of through holes 42e that allow the space in the non-through hole 42d and the receiving hole 11a. The space inside is connected. In other words, the space in the non-through hole 42d communicates with the outside through the through hole 42e, the accommodation hole 11a, the accommodation space 15, and the communication hole 14a.

The end surface 42c of the valve stem 42 is close to and away from the valve body 43. When the end surface 42c is in contact with the valve body 43, the open end of the non-through hole 42d is closed by the valve body 43.

Further, the valve stem 42 is formed with a large diameter portion 42f on the outer circumference of the valve cartridge 41, and a small diameter portion 42g having a small diameter with respect to the large diameter portion 42f is formed continuously with the large diameter portion 42f. On the other hand, the first insertion hole 41d of the valve casing 41 is provided with a reduced diameter portion 41i at a position opposed to the large diameter portion 42f, and an enlarged diameter portion 41j is provided at a position opposed to the small diameter portion 42g.

The flow path resistance is applied to the air flow flowing through the annular gap formed between the large diameter portion 42f and the reduced diameter portion 41i, and the flow path resistance and the flow path length of the annular gap in the direction of the first central axis O1 are The length of the central axis O1 direction large diameter portion 42f overlaps with the reduced diameter portion 41i. Here, the length in which the large diameter portion 42f overlaps with the reduced diameter portion 41i changes in accordance with the displacement amount of the valve stem 42 with respect to the valve case 41. That is, when the displacement of the valve stem 42 relative to the valve casing 41 is relatively small and the flow path length of the annular gap is long, the air does not easily flow, and the displacement of the valve stem 42 relative to the valve casing 41 is relatively large and When the length of the flow path of the annular gap is short, the air easily flows.

Further, a plurality of through holes 41k are formed in the valve casing 41, and the first insertion hole 41d is opened in the enlarged diameter portion 41j and opened on the outer peripheral surface of the valve casing 41, so that the space in the first insertion hole 41d is The passage 11c constituting the air spring passage 6 communicates. In other words, the space surrounded by the outer peripheral surface of the first insertion hole 41d and the valve stem 42 is always in communication with the air spring 3 through the through hole 41k and the passages 11c, 12c, and 11d.

According to the supply/discharge valve 40 having the above configuration, when the end surface 42c of the valve stem 42 is in contact with the valve body 43, and the valve body 43 is seated on the first valve seat portion 41g, the air spring passage 6 communicates with the supply passage 9, And the state in which the communication between the air spring passage 6 and the exhaust passage 8 is blocked.

On the other hand, when the valve stem 42 moves in the direction of entering the valve casing 41 (in the direction of the arrow C in Fig. 2), the valve body 43 is brought from the first valve in a state where the end surface 42c of the valve stem 42 is in contact with the valve body 43. When the seat portion 41g is displaced, the air spring passage 6 communicates with the supply passage 9, and the communication between the air spring passage 6 and the exhaust passage 8 is blocked.

Conversely, in the direction in which the valve stem 42 is withdrawn from the valve casing 41 (in the direction of the arrow D in Fig. 2), the end surface 42c of the valve stem 42 is separated from the valve body 43, and the valve body 43 is seated on the first valve seat portion 41g. At this time, the communication between the air spring passage 6 and the supply passage 9 is blocked, and the air spring passage 6 communicates with the exhaust passage 8.

As such, the supply and discharge valve 40 can selectively communicate the supply passage 9 or the exhaust passage 8 with the air spring passage 6 corresponding to the movement of the valve stem 42 with respect to the valve housing 41, and the supply passage 9 and the exhaust passage 8 It is blocked with respect to the communication of the air spring passage 6.

Next, the piston 20 that moves the valve stem 42 and the rotor 30 that transmits the relative displacement of the vehicle body 1 to the trolley 2 to the piston 20 will be described.

A cylindrical member in which a through hole 20a through which the insertion portion 42b of the valve stem 42 is inserted is formed in the center of the piston 20, and is slidably supported by the receiving hole 11a in the direction of the first central axis O1. As shown in FIG. 3, a guide groove 21 is formed in a part of the outer peripheral surface of the piston 20, and the guide groove 21 has a crescent shape in cross section and is orthogonal to the sliding direction of the piston 20 (the direction of the first central axis O1). The direction has a certain width. Further, a flow path (not shown) that connects the both sides of the piston 20 is formed. Thereby, when the piston 20 moves in the direction of the first central axis O1, the air in the accommodation hole 11a can move through the flow path.

The rotor 30 has a cylindrical body portion 31 and a quadrangular columnar boss portion 32 which is formed to protrude from one end portion of the body portion 31 and has a width smaller than the outer diameter of the body portion 31; The portion 33 is provided at the other end portion of the main body portion 31, and the arm portion 34 is formed to protrude outward in the radial direction from the outer peripheral surface of the flange portion 33.

As shown in FIG. 3, the rotor 30 supports the body portion 31 via the support holes 14b via the bearings 17, 18 provided in the cover member 14. In this manner, the rotor 30 is rotatably supported by the casing 10 around the second central axis O2 extending in the direction orthogonal to the first central axis O1.

Further, a pin 35 is provided in the arm portion 34 of the rotor 30 which is displaced from the second central axis O2 which is the center of rotation of the rotor 30. The pin 35 is press-fitted to the arm portion 34 at one end side, and is attached to the other end side from the arm portion 34. In a state in which the rotor 30 is assembled to the casing 10, as shown in FIG. 3, the other end side of the pin 35 projecting from the arm portion 34 is inserted into the guide groove 21 of the piston 20.

As shown in FIG. 1, the boss portion 32 is fitted to the fitting hole 4a formed in the rod 4. Therefore, when the boss portion 32 is rotated with the rotation of the lever 4, the pin 35 pressed into the arm portion 34 moves in the direction of the arrow E or the arrow F shown in FIG. 2 around the second central axis O2. . Since the pin 35 is in contact with the guide groove 21 of the piston 20, the rotation of the rotor 30 is transmitted to the piston 20 via the pin 35, and the piston 20 is oriented in the receiving hole 11a toward the first central axis O1 as the pin 35 moves (Fig. 2 arrows C, D direction) move.

Further, the horizontal valve 100 further includes a rotation restricting portion 50 that guides the piston 20 in the direction of the first central axis O1 and that restricts the piston 20 from rotating about the first central axis O1. The rotation restricting portion 50 will be described below.

The rotation restricting portion 50 has a restricting plate 51 as a restricting member disposed in the receiving hole 11a of the main casing 11, and a sliding groove 52 as a sliding portion formed on the outer peripheral surface of the piston 20 for the restricting plate 51 sliding.

The limiting plate 51 is a plate-shaped member that extends along the first central axis O1, and has a first end surface 51a that abuts against the insertion portion 12b of the first cover member 12 and a second end surface 51b that abuts The first cylindrical portion 41a of the valve casing 41. As shown in FIG. 3, the cross section of the restricting plate 51 is formed in an arc shape extending in the circumferential direction along the inner circumferential surface of the receiving hole 11a, and the restricting plate 51 has two restricting faces 51c which are equal to the circumferential direction abutting on the sliding joint. The groove 52; the arc-shaped outer surface 51d abuts against the inner circumferential surface of the receiving hole 11a; and the arc-shaped inner surface 51e which is concentric with the outer surface 51d. As described above, since the restricting plate 51 has a circular arc-shaped member, it can be easily formed by cutting the tubular material in the axial direction. Further, the restricting plate 51 can also be formed by bending a flat plate.

The limiting plate 51 of the above-described shape is fixed to the main casing 11 by being interposed between the insertion portion 12b and the first cylindrical portion 41a inserted into the receiving hole 11a. In order to fix the limiting plate 51 at a predetermined position, as shown in FIGS. 2 and 4, a first positioning groove 55 is formed on the outer peripheral surface of the insertion portion 12b. The first positioning groove 55 is formed by the following surfaces: a bottom surface 12d. The first end surface 51a is abutted; the two circumferential direction defining surfaces 12f are opposite to the circumferential direction holding restriction plate 51, and the regulating surfaces 51c are respectively abutted; and the arc-shaped radial predetermined surface 12e is provided. The inner surface 51e abuts. Further, the two circumferential direction defining faces 12f are formed along the radial direction centering on the first central axis O1.

On the other hand, as shown in FIG. 2 and FIG. 5, a second positioning groove 56 is formed on the outer circumferential surface of the first cylindrical portion 41a, and the second positioning groove 56 is provided by the bottom surface 41m to which the second end surface 51b abuts, and The radially defined surface 41n to which the inner surface 51e abuts is formed.

The restricting plate 51, which is inserted into the first positioning groove 55 and the second positioning groove 56 at both ends, is restricted in the circumferential direction by the two circumferential direction defining faces 12f of the first positioning groove 55, and the radially defined surface 12e and the receiving hole are formed. The inner peripheral surface of the 11a is restricted to the radial movement, and the radially defined surface 41n of the second positioning groove 56 and the inner peripheral surface of the receiving hole 11a are restricted from moving in the radial direction. In this manner, the first positioning groove 55 formed in the insertion portion 12b and the second positioning groove 56 formed in the first cylindrical portion 41a restrict the movement of the regulating plate 51 in the circumferential direction and the radial direction, thereby restricting the plate. 51 is positioned relative to the main casing 11.

Further, since the first cylindrical portion 41a is fixed to the main casing 11 by screwing, it is difficult to fix the fixed position in the circumferential direction, and therefore the second positioning groove 56 is formed in an annular shape. Alternatively, when the first cylindrical portion 41a is inserted and fixed to the receiving hole 11a so that the fixed position in the circumferential direction is at a predetermined position, the shape of the second positioning groove 56 may be the same as the first positioning. The groove 55 has the same shape.

In addition, the length of the circumferential direction of the portion in contact with the insertion portion 12b and the first cylindrical portion 41a is set to be longer so that the length of the diagonal line of the restriction plate 51 is longer than the length of the first central axis O1. The restriction plate 51 can be stably clamped and fixed without being inclined in the accommodation hole 11a. Therefore, if the restriction plate 51 is stably fixed in the accommodation hole 11a by making the length of the restriction plate 51 long in the circumferential direction, the restriction plate 51 can be stably fixed in the accommodation hole 11a, and it can be formed in the first cylindrical portion 41a. The second positioning groove 56 is abolished, and the movement of the restricting plate 51 in the circumferential direction and the radial direction is restricted only by the first positioning groove 55.

Further, the thickness of the restricting plate 51 in the radial direction is set in such a manner that the shortest distance L1 from the first central axis O1 to the restricting plate 51 fixed to the main casing 11 is larger than the radius of the pad nut 46 as the coupling member ( 1/2 of the outer diameter D1). By setting the thickness of the restricting plate 51 in the radial direction as described above, it is possible to prevent the coupling member that fastens the piston 20 and the valve stem 42 from interfering with the restricting plate 51.

The sliding groove 52 is formed in a concave shape on the outer circumferential surface of the piston 20 along the first central axis O1, and has two sliding surfaces 52a that sandwich the restriction plate 51 in the circumferential direction. Two planes opposite. The two sliding surfaces 52a are respectively formed along the radial direction centered on the first central axis O1, and the two sliding surfaces 52a are provided with the two limiting faces 51c of the limiting plate 51 along the first central axis O1, respectively. And sliding.

As described above, since the restricting plate 51 is fixed to the main casing 11, even if the piston 20 is biased to rotate about the first central axis O1, the sliding surface 52a abuts against the regulating surface 51c. The piston 20 is prevented from rotating about the first central axis O1. On the other hand, since the sliding surface 52a is slidably supported by the regulating surface 51c, the piston 20 is allowed to smoothly move in the direction of the first central axis O1. Further, if the hardness of the piston 20 and the restricting plate 51 which are in contact with each other are set to the same level, the sticking is likely to occur, so that it is preferable to make the hardness of either one higher than the hardness of the other. For example, in the case where the piston 20 and the restricting plate 51 are formed of the same aluminum alloy, it is preferable to perform a hard aluminum oxide film processing treatment on either one.

The operation of the horizontal valve 100 configured as described above will be described.

When the air load 3 is contracted due to an increase in the load of the vehicle body, that is, when the height of the vehicle body 1 relative to the trolley 2 is lower than a predetermined height, the lever 4 is moved upward from the neutral position (arrow A of FIG. 1). Direction) rises. As the rod 4 is displaced upward, the rotor 30 coupled to the rod 4 is rotated in the direction of the arrow E in FIG. 2 around the second central axis O2, and the pin 35 provided on the arm portion 34 of the rotor 30 is also directed in the direction of the arrow E. mobile. Since the movement of the pin 35 is transmitted to the piston 20 via the guide groove 21, the piston 20 moves in the direction of the arrow C from the neutral position N in Fig. 2 as the pin 35 moves.

When the piston 20 moves in the direction of the arrow C, the valve stem 42 coupled to the piston 20 releases the valve body 43 from the first valve seat portion 41g against the urging force of the spring 45. As a result, the supply passage 9 communicates with the air spring passage 6. Specifically, the compressed air discharged from the compressor 7 passes between the valve body 43 and the first valve seat portion 41g and between the large diameter portion 42f and the reduced diameter portion 41i, and passes through the through hole 41k and the passages 11c and 12c. 11d is supplied to the air spring 3, wherein the compressed air has passed through the passages 11e, 13a, 41h, and 48b, passes between the check valve body 44 and the second valve seat portion 48a, and flows into the second insertion hole 41e. The space inside.

At this time, the end surface 42c of the valve stem 42 is pressed to the valve body 43, so that the open end of the non-through hole 42d is closed by the valve body 43. In other words, when the piston 20 moves from the neutral position N in the direction of the arrow C, the supply valve formed by the first valve seat portion 41g and the valve body 43 is opened, and the supply passage 9 communicates with the air spring passage 6. The discharge valve composed of the valve body 43 and the end surface 42c of the valve stem 42 is in a closed state, and the exhaust passage 8 and the air spring passage 6 are blocked.

As described above, when the supply passage 9 communicates with the air spring passage 6, the compressed air from the compressor 7 is supplied to the air spring 3 through the supply passage 9 and the air spring passage 6, and the air spring 3 is extended. By the extension of the air spring 3, the height of the vehicle body 1 relative to the trolley 2 becomes high, and the lever 4 is also close to the neutral position. As the rod 4 approaches the neutral position, the piston 20 also moves in the direction of the arrow D toward the neutral position N in Fig. 2, and soon, if the height of the vehicle body 1 becomes a predetermined height, the piston 20 reaches the neutral position N. At this time, since the valve body 43 is seated on the first valve seat portion 41g, the supply valve is in a closed state. As a result, the communication between the supply passage 9 and the air spring passage 6 is blocked, and the supply of the compressed air to the air spring 3 is stopped.

On the other hand, when the load of the vehicle body is reduced and the air spring 3 is extended, that is, when the height of the vehicle body 1 with respect to the trolley 2 is higher than a predetermined height, the lever 4 is moved downward from the neutral position ( Pull down in the direction of arrow B of Figure 1. As the rod 4 is displaced downward, the rotor 30 coupled to the rod 4 is rotated in the direction of the arrow F in FIG. 2 around the second central axis O2, and the pin 35 provided on the arm portion 34 of the rotor 30 is also directed in the direction of the arrow F. mobile. Since the movement of the pin 35 is transmitted to the piston 20 via the guide groove 21, the piston 20 moves in the direction of the arrow D from the neutral position N in Fig. 2 as the pin 35 moves.

When the piston 20 moves in the direction of the arrow D, the end surface 42c of the stem 42 coupled to the piston 20 is separated from the valve body 43. As a result, the air spring passage 6 communicates with the exhaust passage 8. Specifically, the compressed air in the air spring 3 passes through the passages 11d, 12c, and 11c and the through hole 41k, passes between the large diameter portion 42f and the reduced diameter portion 41i, and between the valve body 43 and the end surface 42c, and flows into The non-through hole 42d is further released into the atmosphere through the through hole 42e, the receiving hole 11a, the accommodating space 15, and the communication hole 14a.

At this time, the valve body 43 is pressed against the first valve seat portion 41g by the pressing force of the spring 45, so that the space in the second insertion hole 41e and the annular gap between the large diameter portion 42f and the reduced diameter portion 41i are blocked. The state of the break. In other words, when the piston 20 is moved from the neutral position N in the direction of the arrow D, the discharge valve including the valve body 43 and the end surface 42c of the valve stem 42 is opened, and the air spring passage 6 and the exhaust passage 8 are opened. In the communication state, the supply valve composed of the first valve seat portion 41g and the valve body 43 is closed, and the communication between the supply passage 9 and the air spring passage 6 is blocked.

As described above, when the air spring passage 6 communicates with the exhaust passage 8, the compressed air in the air spring 3 is released to the atmosphere through the air spring passage 6 and the exhaust passage 8, and the air spring 3 contracts. By contraction of the air spring 3, the height of the vehicle body 1 relative to the trolley 2 becomes lower, and the lever 4 is also close to the neutral position. As the rod 4 approaches the neutral position, the piston 20 also moves in the direction of the arrow C toward the neutral position N in Fig. 2, and soon, if the height of the vehicle body 1 becomes a predetermined height, the piston 20 reaches the neutral position N. At this time, the end surface 42c of the valve stem 42 abuts against the valve body 43, so that the discharge valve is in a closed state. As a result, the communication between the air spring passage 6 and the exhaust passage 8 is blocked, and the discharge of the compressed air from the air spring 3 is stopped.

In this manner, the horizontal valve 100 adjusts the air spring 3 selectively to the compressor 7 or the atmosphere in accordance with the direction of the rotation of the rod 4, and adjusts the height of the vehicle body 1 relative to the carriage 2 to a predetermined height. The rod 4 is rotated in accordance with the relative displacement of the vehicle body 1 relative to the trolley 2.

Further, when the horizontal valve 100 is actuated as described above, the restricting plate 51 is always used to prevent the piston 20 from rotating about the first central axis O1. Therefore, even if the distance between the rotor 30 and the piston 20 is increased by the wear of the rotor 30 or the like, the displacement of the rotor 30 is transmitted to the piston 20 via the pin 35. As a result, the horizontal valve 100 is stably operated in accordance with the relative displacement of the vehicle body 1 with respect to the carriage 2.

Further, the restricting plate 51 for restricting the rotation of the piston 20 is formed in an arc shape having a specific length in the circumferential direction of the inner peripheral surface of the receiving hole 11a, and has a relatively high cross-sectional shape with respect to the bending moment, so that even The force of the piston 20 rotating about the first central axis O1 is slightly increased and is not easily deformed. Therefore, the restricting plate 51 can stably restrict the rotation of the piston 20 around the first central axis O1.

According to the first embodiment described above, the following effects are exhibited.

In the horizontal valve 100, the restriction piston 51 provided in the casing 10 and the sliding groove 52 provided in the piston 20 restrict the rotation of the piston 20 around the first central axis O1 of the accommodation hole 11a. In this way, the piston 20 is prevented from rotating, so that the displacement of the rotor 30 is always transmitted to the piston 20 normally. As a result, the horizontal valve 100 can be stably operated.

Further, in the horizontal valve 100, the restricting plate 51 is formed of a member different from the casing 10. Therefore, by forming the sliding groove 52 and assembling the restricting plate 51 for the existing horizontal valve 100, the rotation of the piston 20 can be easily prevented.

Further, in the first embodiment described above, the regulating plate 51 is formed of a member different from the casing 10. Alternatively, the regulating plate 51 may be integrally formed with the casing 10, and a projecting portion having an arcuate cross section that protrudes from the inner peripheral surface of the receiving hole 11a may be provided as a regulating member. In this case, it is not necessary to process the first positioning groove 55 and the second positioning groove 56 of the holding plate 51 in the insertion portion 12b and the first cylindrical portion 41a, respectively, and the number of parts is reduced, so that the manufacture of the horizontal valve 100 can be reduced. cost.

Next, a modification of the horizontal valve 100 according to the first embodiment of the present invention will be described with reference to Figs. 6 to 9 . Fig. 6 is a cross-sectional view showing a modification of the portion corresponding to Fig. 3, Fig. 7 is a cross-sectional view showing a modification of the portion corresponding to Fig. 4, and Fig. 8 is a cross-sectional view showing a modification of the portion corresponding to Fig. 5. Further, Fig. 9 is an enlarged view of a cross section taken along the line IX-IX of Fig. 8.

In the first embodiment described above, the restriction plate 51 having an arcuate cross section is used as the restriction member. Instead, a rod-shaped member-restricting rod 53 having a circular cross-sectional shape may be used as the restricting member.

In this case, the regulating rod 53 is supported by the positioning groove 57 formed in the insertion portion 12b and the positioning hole 58 formed in the first cylindrical portion 41a. Specifically, as shown in FIG. 7 , the positioning groove 57 has a bottom surface 12 d that abuts against the first end surface 53 a of one end side of the regulating rod 53 , and two circumferential direction defining surfaces 12 f that sandwich the restriction rod 53 and the like. The outer peripheral surface 53c of the regulating rod 53 is abutted in parallel, and the radially defined surface 12e is abutted by the outer peripheral surface 53c of the regulating rod 53. Further, as shown in FIGS. 8 and 9, the positioning hole 58 has a support hole 41p opened at the end surface of the first cylindrical portion 41a, and the second end surface 53b of the other end side of the restriction rod 53 abuts against the support hole 41p. Bottom surface.

The support hole 41p is formed with a plurality of non-through holes in the circumferential direction around the first central axis O1, and has an inner diameter slightly larger than the end portion of the restricting rod 53. Further, a tapered portion 41r whose diameter gradually increases toward the opening side is provided on the opening end side of the support hole 41p. The tapered portion 41r provided in the adjacent support hole 41p is formed so that the open ends overlap each other.

Here, since the first cylindrical portion 41a supporting the other end side of the regulating rod 53 is fixed to the main casing 11 by screwing, it is difficult to always fix the fixed position in the circumferential direction. Therefore, as described above, a plurality of support holes 41p are formed in the circumferential direction around the first central axis O1, whereby the restriction rod 53 is inserted into the state in which the first cylindrical portion 41a is fixed to the main casing 11. The support hole 41p is at the position closest to the prescribed position.

Further, when the restriction rod 53 is inserted into the support hole 41p, the tapered portion 41r functions as a guide portion that guides the other end portion of the restriction rod 53 to the support hole 41p. Therefore, when the regulating rod 53 is moved so as to be disposed at a predetermined position toward the first cylindrical portion 41a, the regulating rod 53 is guided to the support hole 41p closest to the predetermined position.

The restricting rods 53 which are respectively inserted into the positioning grooves 57 and the positioning holes 58 are restricted from the circumferential movement by the two circumferential direction defining faces 12f of the positioning grooves 57, and are restricted by the radially defined faces 12e and the inner peripheral faces of the receiving holes 11a. It moves in the radial direction and is restricted by the positioning hole 58 in the circumferential direction and the radial movement. In this manner, the positioning groove 57 formed in the insertion portion 12b and the positioning hole 58 formed in the first cylindrical portion 41a restrict the movement of the regulating rod 53 in the circumferential direction and the radial direction, thereby restricting the regulating rod 53 to the main portion. Positioned by the casing 11.

Further, the diameter of the restricting rod 53 is set in such a manner that the shortest distance L2 from the first central axis O1 to the outer peripheral surface 53c of the restricting rod 53 positioned in the main casing 11 is larger than the radius of the pad nut 46 as the coupling member. (1/2 of the outer diameter D1). By setting the diameter of the restricting rod 53 in this way, it is possible to prevent the coupling member that fastens the piston 20 and the valve stem 42 from interfering with the restricting rod 53.

The sliding groove 54 is formed in a concave shape on the outer circumferential surface of the piston 20 along the first central axis O1, and has two sliding surfaces 54a that sandwich the restriction rod 53 and oppose it. Two planes. The two sliding surfaces 54a are formed in parallel with each other, and the two sliding surfaces 54a are slidably attached to the outer peripheral surface 53c of the regulating rod 53 along the first central axis O1.

As described above, since the restricting rod 53 is fixed to the main casing 11, even if the piston 20 is biased to rotate about the first central axis O1, the retaining rod 53 abuts against the restricting rod 53 by the sliding surface 54a. The outer peripheral surface 53c prevents the piston 20 from rotating about the first central axis O1. On the other hand, since the sliding surface 54a is slidably supported by the outer peripheral surface 53c of the regulating rod 53, the piston 20 is allowed to smoothly move in the direction of the first central axis O1. Further, the pistons 20 and the restricting bars 53 that are slidably coupled to each other are set such that the hardness of either one is higher than the hardness of the other.

Thus, even when the restricting rod 53 is used as the restricting member, the piston 20 can be restricted by the restricting rod 53 provided in the casing 10 and the sliding groove 54 provided in the piston 20 to accommodate the first hole 11a. The central axis O1 rotates centering.

 <Second embodiment>  

Next, a horizontal valve 200 according to a second embodiment of the present invention will be described with reference to Fig. 10 . In the following, the differences from the first embodiment will be mainly described, and the same components as those in the first embodiment will be denoted by the same reference numerals and will not be described.

The basic configuration of the horizontal valve 200 is the same as that of the horizontal valve 100 of the first embodiment. The horizontal valve 200 is different from the horizontal valve 100 in that the rotation restricting portion 150 has a restricting member 151 disposed on the piston 20 and a sliding groove 152 as a sliding portion provided in the housing 10, The restricting member 151 is slidably connected.

The restricting member 151 is formed into a rectangular parallelepiped shape and is assembled to the outer peripheral surface of the piston 20 along the direction of the first central axis O1. Specifically, the restricting member 151 is press-fitted and fixed to the groove 22 formed on the outer peripheral surface of the piston 20 along the first central axis O1 so that a part thereof protrudes from the outer peripheral surface of the piston 20 . The restricting member 151 is provided with two restricting faces 151a formed in parallel with each other in the direction of the first central axis O1 from a portion protruding from the outer peripheral surface of the piston 20. A portion of the restricting member 151 in which the two restricting faces 151a are formed is housed in the sliding groove 152.

The radial depth of the groove 22 into which the restricting member 151 is pressed is set in such a manner that the shortest distance L3 from the first central axis O1 to the restricting member 151 fixed to the groove 22 is larger than that of the pad nut 46 as the coupling member. Radius (1/2 of the outer diameter D1). By thus setting the radial depth of the groove 22, the joint member that fastens the piston 20 and the valve stem 42 can be prevented from interfering with the restricting member 151.

The sliding groove 152 is formed in a concave shape on the inner circumferential surface of the receiving hole 11a along the direction of the first central axis O1, and has two sliding surfaces 152a that sandwich the restricting member 151. Two planes opposite. The two sliding surfaces 152a are formed in parallel with each other, and the two sliding surfaces 152a are respectively slidably supported by the regulating faces 151a of the regulating members 151 along the first central axis O1.

As described above, since the restricting member 151 is fixed to the piston 20, even if the piston 20 is biased to rotate about the first central axis O1, the sliding contact surface 152a abuts against the restricting member 151. The surface 151a prevents the piston 20 from rotating about the first central axis O1. On the other hand, since the regulating surface 151a is slidably supported by the sliding surface 152a, the piston 20 is allowed to smoothly move along the direction of the first central axis O1 in which the sliding groove 152 is formed. Further, the restricting members 151 and the main casing 11 that are slidably coupled to each other are set such that the hardness of either one is higher than the hardness of the other.

Thus, even when the restricting member 151 is provided in the piston 20, the piston 20 can be restrained by the first and second holes of the receiving hole 11a by the sliding groove 152 provided in the casing 10 and the restricting member 151 provided in the piston 20. The central axis O1 rotates centering.

The operation of the horizontal valve 200 is the same as that of the horizontal valve 100 of the above-described first embodiment, and thus the description thereof is omitted.

When the horizontal valve 200 is actuated, as described above, the restricting member 151 is always used to prevent the piston 20 from rotating about the first central axis O1. Therefore, even if the distance between the rotor 30 and the piston 20 is increased by the wear of the rotor 30 or the like, the displacement of the rotor 30 is transmitted to the piston 20 via the pin 35. As a result, the horizontal valve 200 is stably operated in accordance with the relative displacement of the vehicle body 1 with respect to the carriage 2.

According to the second embodiment described above, the following effects are exhibited.

In the horizontal valve 200, the piston 20 is rotated around the first central axis O1 of the accommodation hole 11a by the sliding groove 152 provided in the casing 10 and the regulating member 151 provided in the piston 20. In this way, the piston 20 is prevented from rotating, so that the displacement of the rotor 30 is always transmitted to the piston 20 normally. As a result, the horizontal valve 200 can be stably operated.

Further, in the horizontal valve 200, the restricting member 151 is formed of a member different from the casing 10 and the piston 20. Therefore, by forming the sliding groove 152 for the existing horizontal valve 200 and forming the groove 22 for fixing the restricting member 151, the rotation of the piston 20 can be easily prevented.

Further, in the second embodiment, the restricting member 151 is press-fitted and fixed to the groove 22 formed in the piston 20, and the sliding groove 152 is formed on the inner circumferential surface of the housing hole 11a of the casing 10. Alternatively, the restricting member 151 may be press-fitted and fixed to a groove formed in the inner circumferential surface of the accommodation hole 11a, and the sliding groove 152 may be provided on the outer circumferential surface of the piston 20.

Further, in the second embodiment described above, the regulating member 151 is formed of a member different from the piston 20. Alternatively, the restricting member 151 may be integrally formed with the piston 20, and a protruding portion having a rectangular cross section that protrudes from the outer peripheral surface of the piston 20 may be provided as the restricting member. In this case, it is not necessary to process the groove 22 for fixing the restricting member 151, and the number of parts is reduced, so that the manufacturing cost of the horizontal valve 200 can be reduced.

 <Third embodiment>  

Next, a horizontal valve 300 according to a third embodiment of the present invention will be described with reference to Fig. 11 . In the following, the differences from the first embodiment will be mainly described, and the same components as those in the first embodiment will be denoted by the same reference numerals and will not be described.

The basic configuration of the horizontal valve 300 is the same as that of the horizontal valve 100 of the first embodiment. The horizontal valve 300 is different from the horizontal valve 100 in that the rotation restricting portion 250 has a restricting plate 251 as a restricting member that is fixed to the inner peripheral surface of the housing hole 11a of the housing 10; The joint portion 252 is disposed on the outer circumferential surface of the piston 20 for restricting the sliding of the flat plate 251.

The restriction flat plate 251 is a flat member having a specific thickness and is fixed to the inner circumferential surface of the accommodation hole 11a along the direction of the first central axis O1. Specifically, the restriction plate 251 is press-fitted and fixed so as to be entirely accommodated in the accommodation groove 11g formed in the inner circumferential surface of the accommodation hole 11a along the direction of the first central axis O1. The length of the restriction flat plate 251 in the direction of the first central axis O1 is set so as to exceed the range in which the piston 20 moves in the direction of the first central axis O1. The surface of the regulating plate 251 opposed to the sliding portion 252 provided on the piston 20 is provided with a regulating surface 251a as a flat portion of the contact sliding portion 252.

The thickness of the restriction plate 251 and the radial depth of the accommodation groove 11g of the accommodation regulating plate 251 are set such that the shortest distance L4 from the first central axis O1 to the restriction plate 251 accommodated in the accommodation groove 11g is larger than that as the coupling member. The radius of the pad nut 46 (1/2 of the outer diameter D1). By thus limiting the thickness of the flat plate 251 and the depth of the receiving groove 11g, it is possible to prevent the coupling member that fastens the piston 20 and the valve stem 42 from interfering with the restriction plate 251.

The sliding portion 252 is formed in a planar shape on the outer circumferential surface of the piston 20 along the direction of the first central axis O1, and has a sliding surface 252a which is attached to the regulating surface 251a of the restricting plate 251 in the radial direction. To the plane. The sliding surface 252a is slidably supported by the regulating surface 251a of the regulating plate 251 in the direction of the first central axis O1.

As described above, since the restricting plate 251 is fixed to the casing 10, even if the piston 20 is biased to rotate about the first central axis O1, the sliding plate 252a is abutted against the restricting plate 251. The regulating surface 251a prevents the piston 20 from rotating about the first central axis O1. On the other hand, since the sliding surface 252a is slidably supported by the regulating surface 251a, the piston 20 is allowed to smoothly move along the direction of the first central axis O1 in which the regulating plate 251 is provided. Further, the restricting plate 251 and the piston 20 that are slidably coupled to each other are set such that the hardness of either one is higher than the hardness of the other.

In this way, even when the restricting member is a flat member fixed to the receiving hole 11a, the piston 20 can be restricted by the restricting plate 251 provided in the housing 10 and the sliding portion 252 provided on the piston 20. The first central axis O1 of the accommodation hole 11a rotates around the center.

The operation of the horizontal valve 300 is the same as that of the horizontal valve 100 of the above-described first embodiment, and thus the description thereof is omitted.

When the horizontal valve 300 is actuated, as described above, the restricting plate 251 is always used to prevent the piston 20 from rotating about the first central axis O1. Therefore, even if the distance between the rotor 30 and the piston 20 is increased by the wear of the rotor 30 or the like, the displacement of the rotor 30 is transmitted to the piston 20 via the pin 35. As a result, the horizontal valve 300 is stably operated in accordance with the relative displacement of the vehicle body 1 with respect to the carriage 2.

According to the third embodiment described above, the following effects are exhibited.

In the horizontal valve 300, the restriction plate 251 provided in the casing 10 and the sliding portion 252 provided in the piston 20 restrict the piston 20 from rotating around the first central axis O1 of the accommodation hole 11a. In this way, the piston 20 is prevented from rotating, so that the displacement of the rotor 30 is always transmitted to the piston 20 normally. As a result, the horizontal valve 300 can be stably operated.

Further, in the horizontal valve 300, the regulating plate 251 is formed of a member different from the casing 10. Therefore, by forming the accommodation groove 11g for accommodating the restriction plate 251 with the existing horizontal valve 300 and forming the sliding surface 252a on the outer circumferential surface of the piston 20, the rotation of the piston 20 can be easily prevented.

Further, in the third embodiment described above, the restriction plate 251 is formed of a member different from the casing 10. Alternatively, the regulating plate 251 may be integrally formed with the casing 10, and a flat portion formed on the inner circumferential surface of the receiving hole 11a may be provided as a regulating member. In this case, it is not necessary to process the housing groove 11g of the accommodation regulating plate 251, and the number of parts is reduced, so that the manufacturing cost of the horizontal valve 300 can be reduced.

The constitution, operation, and effects of the embodiments of the present invention configured as described above will be summarized and summarized.

The horizontal valves 100, 200, and 300 include a casing 10 formed with an air spring passage 6 communicating with the air spring 3, and a piston 20 slidably housed in the housing hole 11a formed in the casing 10, and corresponding to The vehicle body 1 moves in the receiving hole 11a with respect to the relative displacement of the carriage 2; and the rotation restricting portions 50, 150, 250 are provided in the casing 10 and the piston 20, along the first central axis of the receiving hole 11a. The piston 20 is guided in the O1 direction, and the restriction piston 20 is rotated about the first central axis O1.

According to this configuration, the rotation restricting portions 50, 150, and 250 provided in the casing 10 and the piston 20 allow the piston 20 to move in the direction of the first central axis O1 of the accommodation hole 11a, and the piston 20 is restricted to the first center. The shaft O1 rotates centering. As described above, the rotation of the piston 20 around the first central axis O1 is prevented, so that the displacement of the rotor 30 is always transmitted to the piston 20 normally. As a result, the horizontal valves 100, 200, and 300 can be stably operated.

Further, the rotation restricting portions 50, 150, and 250 have restricting members 51, 53, 151, and 251 which are provided in any one of the housing 10 and the piston 20, and the sliding portions 52, 54, 152, 252, The other of the casing 10 and the piston 20 is slidably coupled to the restricting members 51, 53, 151, and 251 in the direction of the first central axis O1; and the rotating system of the piston 20 is centered on the first central axis O1. It is restricted by the abutment of the restricting members 51, 53, 151, 251 and the sliding portions 52, 54, 152, 252.

According to this configuration, the restricting members 51, 53, 151, and 251 provided in any one of the casing 10 and the piston 20, and the sliding portion 52 provided to the other of the casing 10 and the piston 20, 54, 152, and 252, the piston 20 is allowed to move in the direction of the first central axis O1 of the accommodation hole 11a, and the restriction piston 20 is rotated about the first central axis O1. As described above, the rotation of the piston 20 around the first central axis O1 is prevented, so that the displacement of the rotor 30 is always transmitted to the piston 20 normally. As a result, the horizontal valves 100, 200, and 300 can be stably operated.

Further, the sliding portions 52, 54 and 152 are formed in a concave shape on the outer circumferential surface of the piston 20 or the inner circumferential surface of the accommodation hole 11a along the first central axis O1, and have the clamp restricting members 51, 53, 151 and To the two planes 52a, 54a, 152a, and the rotation of the piston 20 about the first central axis O1 is abutted by the restriction members 51, 53, 151 by either of the two planes 52a, 54a, 152a. And is limited.

According to this configuration, even if the piston 20 is biased to rotate about the first central axis O1, any one of the two flat surfaces 52a, 54a, and 152a and the restricting members 51, 53, 151 The piston 20 is prevented from rotating about the first central axis O1. As a result, the displacement of the rotor 30 is always transmitted to the piston 20 normally, so that the horizontal valves 100, 200 can be stably operated.

Further, the horizontal valve 100 further includes an insertion portion 12b of the first cover member 12 that is inserted into one end side of the accommodation hole 11a, and a first cylindrical portion 41a of the valve case 41 that is inserted into the other end side of the accommodation hole 11a. The restriction members 51 and 53 are disposed in the accommodation hole 11a along the first central axis O1, and both ends of the restriction members 51 and 53 are supported by the insertion portion 12b and the first cylindrical portion 41a.

According to this configuration, the regulating members 51 and 53 are held by the insertion portion 12b and the first cylindrical portion 41a in the accommodation hole 11a. In this manner, the restriction members 51 and 53 that restrict the rotation of the piston 20 can be fixed to a predetermined position in the accommodation hole 11a by a simple configuration. Further, since the restricting members 51 and 53 are formed of members different from the casing 10 and the piston 20, the assembly of the assembly restricting members 51 and 53 is performed on the existing horizontal valve 100, whereby the rotation of the piston 20 can be easily prevented.

Further, the movement of the regulating members 51 and 53 in the circumferential direction and the radial direction about the first central axis O1 is restricted by at least one of the insertion portion 12b and the first cylindrical portion 41a.

According to this configuration, the movement of the regulating members 51 and 53 in the circumferential direction and the radial direction is restricted by at least one of the insertion portion 12b and the first cylindrical portion 41a. As described above, the restriction members 51 and 53 that restrict the rotation of the piston 20 are surely prevented from moving in the circumferential direction or the radial direction from the predetermined position. Therefore, the piston 20 can be more reliably prevented from rotating about the first central axis O1.

Moreover, the regulating member 51 is a member formed in an arc shape along the circumferential direction of the inner circumferential surface of the accommodation hole 11a.

According to this configuration, the regulating member 51 is formed of a member having an arcuate cross section extending along the first central axis O1. In this way, the restricting member 51 has a cross-sectional shape having a relatively high rigidity with respect to the bending moment. Therefore, even if the force of the rotation of the piston 20 around the first central axis O1 is slightly increased, it is less likely to be deformed. As a result, it is possible to more reliably prevent the piston 20 from rotating about the first central axis O1.

Further, the restricting member 51 is formed by cutting the tube in the axial direction.

According to this configuration, the restricting member 51 is formed of a member having a circular arc shape extending along the first central axis O1. Therefore, the restricting member 51 can be easily and inexpensively formed by cutting the tubular material in the axial direction.

Further, the sliding portion 252 has a sliding surface 252a formed in a planar shape on the outer circumferential surface of the piston 20 along the first central axis O1, and the regulating member 251 is provided in the casing 10, and has a regulating surface 251a. 251a is formed in a planar shape along the first central axis O1 and faces the sliding surface 252a. The rotation of the piston 20 about the first central axis O1 is abutted by the sliding surface 252a and the regulating surface 251a. Is limited.

According to this configuration, even if the piston 20 is biased to rotate about the first central axis O1, the sliding surface 252a provided on the piston 20 abuts against the regulating surface 251a provided on the casing 10. The piston 20 is prevented from rotating about the first central axis O1. By providing the piston 20 and the casing 10 with a simple configuration of the opposing planes as described above, it is possible to reliably prevent the piston 20 from rotating about the first central axis O1.

Further, the regulating members 51, 151, and 251 are integrally formed with any of the casing 10 and the piston 20.

According to this configuration, the regulating members 51, 151, and 251 are integrally formed with any of the casing 10 and the piston 20. Therefore, it is not necessary to perform processing of the grooves or the like for fixing the regulating members 51, 151, and 251, and the number of parts is reduced, so that the manufacturing cost of the horizontal valves 100, 200, and 300 can be reduced.

Further, the horizontal valves 100, 200, and 300 further include a valve stem 42 that is fixed to the piston 20 and extends along the first central axis O1, and a pad nut 46 that couples the piston 20 to the valve stem 42; The shortest distances L1, L2, L3, and L4 of the first central axis O1 to the restricting members 51, 53, 151, and 251 are larger than the maximum radius of the pad nut 46 centering on the first central axis O1.

According to this configuration, the shortest distances L1, L2, L3, and L4 of the first central axis O1 to the regulating members 51, 53, 151, and 251 are set to be larger than the maximum radius of the pad nut 46 centering on the first central axis O1. By setting the shortest distances L1, L2, L3, and L4 of the first central axis O1 to the restricting members 51, 53, 151, and 251 in this way, it is possible to prevent the coupling member and the like of the pad nut 46 that couples the piston 20 and the valve stem 42 The members 51, 53, 151, 251 interfere.

The embodiments of the present invention have been described above, but the above embodiments are merely illustrative of the application examples of the present invention, and are not intended to limit the technical scope of the present invention to the specific configuration of the above embodiments.

For example, in each of the above embodiments, the valve stem 42 is slidably supported by only one end, but the both ends may be slidably supported. In this case, both ends of the valve stem 42 are slidably supported by the valve casing 41 and the first cover member 12, respectively.

The priority of the Japanese Patent Application No. 2017-012793, filed on Jan. 27,,,,,,,,,,,,,,,

Claims (10)

 A horizontal valve that adjusts a height of an air spring disposed between a vehicle body and a trolley of a vehicle, and includes: a casing formed with an air spring passage communicating with the air spring; and a piston slidably slidably received And being disposed in the receiving hole of the casing and moving in the receiving hole corresponding to a relative displacement amount of the vehicle body with respect to the trolley; and a rotation restricting portion provided on the casing and the piston along The piston is guided in the central axis direction of the accommodation hole, and the piston is restricted from rotating about the central axis.    The horizontal valve according to claim 1, wherein the rotation restricting portion has: a restricting member provided in any one of the casing and the piston; and a sliding portion provided in the casing and the piston The other one is slidably coupled to the restricting member in the central axis direction; and the rotation of the piston about the central axis is restricted by the restricting member contacting the sliding portion.    The horizontal valve according to claim 2, wherein the sliding portion is formed in a concave shape along an outer circumferential surface of the piston or an inner circumferential surface of the receiving hole along the central axis, and is opposed to each other via the restricting member. The two planes, and the rotation of the piston centered on the central axis, are restricted by abutting the restriction member by either of the two planes.    The horizontal valve according to claim 2 or 3, further comprising: a first support portion inserted into one end side of the accommodation hole; and a second support portion inserted into the other end side of the accommodation hole; The restricting member is disposed in the receiving hole along the central axis direction, and both ends of the restricting member are supported by the first support portion and the second support portion.    The horizontal valve according to claim 4, wherein the movement of the restricting member in the circumferential direction and the radial direction about the central axis is restricted by at least one of the first support portion and the second support portion.    The horizontal valve according to claim 4 or 5, wherein the restricting member is a member having a circular arc shape formed along a circumferential direction of an inner circumferential surface of the receiving hole.    The horizontal valve according to claim 6, wherein the restricting member is formed by cutting the tube in the axial direction.    The horizontal valve according to claim 2, wherein the sliding portion has a flat surface formed on the outer circumferential surface of the piston along the central axis, and the restricting member is disposed on the housing and has a flat portion, the plane The portion is formed in a planar shape along the central axis and faces the plane; and the rotation of the piston about the central axis is restricted by the planar surface contacting the planar portion.    The horizontal valve according to any one of claims 2, 3 or 8, wherein the restricting member is integrally formed with any one of the housing and the piston.    The horizontal valve according to any one of claims 2 to 9, further comprising: a rod member fixed to the piston and extending along the central axis; and a coupling member that causes the piston and the rod member And a shortest distance from the central axis to the restricting member is greater than a maximum radius of the coupling member centered on the central axis.