TWI526350B - Horizontal valve - Google Patents

Description

Horizontal valve

The present invention is directed to a leveling valve.

In the patent document JP 2013-173438 A, a horizontal valve for adjusting the height of an air spring used for a railway vehicle is disclosed. a horizontal valve corresponding to a rotation direction of a rocker that rotates according to a relative displacement of the vehicle body with respect to the trolley, and selectively connects the air spring to the compressor or the exhaust passage to maintain the vehicle body at A certain height.

The horizontal valve includes an air supply valve that switches the communication between the air spring and the compressor, an exhaust valve that switches the communication between the air spring and the exhaust passage, and an actuating arm that transmits the swing of the rocker through the buffer spring.

The air supply valve and the exhaust valve respectively have a cylindrical sleeve and a valve body that is slidably disposed in the sleeve. The valve body of the air supply valve is biased in the valve closing direction by the air pressure of the compressor, and the valve body of the air discharge valve is biased toward the valve closing direction by the air pressure of the air spring. The actuator arm is rotated by the restoring force of the buffer spring that is deformed by the rotation of the rocker, and the valve body of the air supply valve or the exhaust valve is pressed to open the air supply valve or the exhaust valve.

In the above-described horizontal valve, if the flow path area is enlarged in order to increase the flow rate of the air supply valve and the exhaust valve, the pressure receiving area of the valve body becomes large, and therefore it is necessary to open the valve against the air pressure. In the direction of the spring pressure valve body, the pressing force of the boom is increased. Actuate the arm by following the rocker The restoring force of the buffer spring that is rotated and deformed is rotated, so it is necessary to increase the size of the buffer spring as well. As a result, the valve case for accommodating the buffer spring is increased in size and the size of the horizontal valve is increased.

It is an object of the present invention to provide a horizontal valve that can expand a flow path area without increasing a size of a buffer spring.

According to an aspect of the present invention, a horizontal valve for adjusting a height of an air spring disposed between a body of a railway vehicle and a trolley includes: a rocker that is rotated corresponding to a relative displacement of the vehicle body with respect to the trolley Actuating arm, which is rotated by the restoring force of the buffer spring deformed by the rotation of the rocker; and the connecting valve is operated by the rotation of the arm to resist the air pressure and open the valve, and The air spring passage connected to the air spring is connected to the compressed air source or the exhaust passage; the connecting valve has a first valve body that presses the actuator arm and moves in the valve opening direction as the writing arm rotates; the second valve body, a first valve seat for the first valve body to be seated and seated, and a sleeve for arranging the first valve body and the second valve body to be slidable therein, and having the second valve body away from the seat The second valve seat having a ring shape and the engagement portion are provided in the second valve body, and when the first valve body is opened after the valve is opened, the first valve body is engaged with the first valve body to merge the second valve body with the first valve body. The first valve body moves together in the valve opening direction; the pressure area of the second valve body is larger than the pressure receiving area of the first valve body

1‧‧‧ body

2‧‧‧Trolley

3‧‧‧Air spring

4‧‧‧ rocker

5‧‧‧Connecting rod

6‧‧‧Air spring passage

7‧‧‧Compressor

8‧‧‧ exhaust passage

9‧‧‧Connected Road

10‧‧‧Contact Path

11‧‧‧Valve

12‧‧‧ oil room

13‧‧‧ Washer

20‧‧‧buffer spring section

21‧‧‧Axis

22‧‧‧Betting arm

23‧‧‧buffer spring

25‧‧‧ oil damper

31‧‧‧Air supply valve

32‧‧‧Exhaust valve

33‧‧‧ sleeve

34‧‧‧1st valve body

35‧‧‧2nd valve body

41‧‧‧ occlusion components

42‧‧‧Helical spring

43‧‧‧Spring bearing member

44‧‧‧1st air chamber

45‧‧‧2nd gas chamber

46‧‧‧Low-voltage interface

47‧‧‧High voltage interface

48‧‧‧1st circular path

49‧‧‧2nd circular path

100‧‧‧ horizontal valve

11a‧‧‧ valve receiving hole

11b‧‧‧Mask thread

33a‧‧‧ Male thread department

33b‧‧‧锷

33c‧‧‧1 hole

33d‧‧‧2nd hole

33e‧‧‧3rd hole

33f‧‧‧4th hole

33g‧‧‧2nd seat

34a‧‧‧Sliding section

34b‧‧‧ Body Department

34c‧‧‧

34d‧‧‧1st reduced diameter

34e‧‧‧2nd reduction

35a‧‧‧1st seat

35b‧‧‧ Body Department

35c‧‧‧Department

35d‧‧‧ connection path

35e‧‧‧Seat

35f‧‧‧Clock Department

35g‧‧‧through hole

55d‧‧‧ Connection path

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

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

Figure 3 is an enlarged view of the exhaust valve.

Fig. 4A is a cross-sectional view showing a section taken along line 4A-4A of Fig. 3.

Fig. 4B is a cross-sectional view showing a section taken along line 4B-4B of Fig. 3.

Fig. 5 is a cross-sectional view showing the state in which the first valve body of the exhaust valve is opened.

Fig. 6 is a cross-sectional view showing a state in which the second valve body of the exhaust valve is opened.

Fig. 7 is a cross-sectional view showing a modification of the second valve body.

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

Fig. 1 is a view showing the mounting of the horizontal valve 100 in the present embodiment.

The horizontal valve 100 has a function of adjusting the height of the air spring 3 provided between the vehicle body 1 of the railway vehicle and the carriage 2 to maintain the vehicle body 1 at a constant height.

The horizontal valve 100 is installed over the vehicle body 1 and the trolley 2. Specifically, the horizontal valve 100 is attached to the vehicle body 1 and is coupled to the trolley 2 via the rocker 4 and the 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 change can be transmitted to the horizontal valve 100 through the connecting rod 5 and the rocker 4.

When the load of the vehicle body increases and the air spring 3 flexes, the rocker 4 is pressed upward from the neutral position (swing in the direction of the arrow A in Fig. 1), and accordingly, the air supply valve 31 of the horizontal valve 100 (refer to 2) The valve is opened, and the air spring passage 6 communicating with the air spring 3 communicates with the compressor 7 as a source of compressed air. Thereby, the compressed air from the compressor 7 is supplied to the air spring 3. When the air spring 3 is restored to a certain height, the rocker 4 returns to the neutral position to close the air supply valve 31 of the horizontal valve 100, thereby blocking the supply of compressed air.

On the other hand, in the case where the load on the vehicle body is reduced and the air spring 3 is extended, the rocker 4 is pulled downward from the neutral position (swing in the direction of the arrow B in Fig. 1), and accordingly, the exhaust of the horizontal valve 100 The valve 32 (see FIG. 2) is opened, and the air spring passage 6 communicates with the exhaust passage 8. Due to exhaust The passage 8 communicates with the atmosphere, so that the compressed air of the air spring 3 is discharged to the atmosphere. When the air spring 3 is restored to a constant height, the rocker 4 returns to the neutral position to close the exhaust valve 32 of the horizontal valve 100, thereby blocking the discharge of the compressed air.

Thus, the horizontal valve 100 selectively connects the air spring 3 to the compressor 7 or the exhaust passage 8 according to the direction of rotation of the rocker 4 that is rotated corresponding to the relative displacement of the vehicle body 1 with respect to the carriage 2. This automatically adjusts the relative displacement generated between the vehicle body 1 and the trolley 2 to maintain the vehicle body 1 at a certain height.

Fig. 2 is a cross-sectional view showing the horizontal valve 100 in the present embodiment. FIG. 3 is an enlarged view of the exhaust valve 32. Fig. 4A is a cross-sectional view showing a section taken along line 4A-4A of Fig. 3. Fig. 4B is a cross-sectional view showing a section taken along line 4B-4B of Fig. 3.

The horizontal valve 100 includes a buffer spring portion 20 disposed at a center portion, an air supply valve 31 and an exhaust valve 32 as a connection valve disposed at an upper portion, and an oil damper 25 disposed at a lower portion.

The buffer spring portion 20 includes a swing arm (not shown) that is fixed to the shaft 21 to which the rocker 4 is coupled, the actuator arm 22 that is freely rotatable with respect to the shaft 21, and the buffer spring 23 that is initially provided. The shaft 21 is inserted concentrically in the state of the load and is disposed in contact with the swing arm and the actuating arm 22 at the same time. The rotation of the rocker 4 is transmitted to the actuator 22 through the swing arm and the buffer spring 23. That is, the actuator arm 22 is rotated by the restoring force of the buffer spring 23 which is deformed by the rotation of the rocker 4.

The oil damper 25 includes a piston (not shown) that is coupled to the proximal end side of the actuator arm 22 and that moves in accordance with the rotation of the writing arm 22. The piston is disposed so as to be immersed in the oil chamber 12 formed in the valve casing 11, and is actuated to the boom 22 when the actuator arm 22 is rotated from the neutral position. The rotation action imparts resistance, and on the other hand, when the actuator arm 22 returns to the neutral position, almost no resistance is applied to the actuator 22.

Hereinafter, the air supply valve 31 and the exhaust valve 32 will be described. Since the configuration of the air supply valve 31 and the exhaust valve 32 is the same, the exhaust valve 32 will be mainly described below. In addition, the same components in the air supply valve 31 and the exhaust valve 32 are denoted by the same reference numerals.

The air supply valve 31 and the exhaust valve 32 are disposed symmetrically about the front end side of the boom 22, and are housed in the valve box 11. A pair of valve accommodation holes 11a are formed in the valve casing 11, and the pair of valve accommodation holes 11a are open to the outside of the valve casing 11 at one end and open to the oil chamber 12 at the other end. Each of the air supply valve 31 and the exhaust valve 32 is housed in the valve housing hole 11a.

The exhaust valve 32 includes a substantially cylindrical sleeve 33 that is fastened in the valve housing hole 11a, and the first valve body 34 is slidably disposed in the sleeve 33 and is rotated with the writing arm 22 The second valve body 35 is slidably disposed in the sleeve 33, and is provided in an annular shape on the outer circumference of the first valve body 34, and the first valve body 34 is seated and seated. The first valve seat 35a.

The male screw portion 33a is formed in one of the outer peripheral surfaces of the sleeve 33, and the male screw portion 33a is screwed to the female screw portion 11b formed on the inner circumference of the valve housing hole 11a, thereby fastening the sleeve 33 to the valve. The inside of the housing hole 11a. Further, a flange portion 33b extending in the radial direction is formed on the outer circumference of the sleeve 33, and the flange portion 33b is in contact with the outer circumferential surface of the valve casing 11 through the gasket 13, whereby the sleeve 33 is positioned in the valve housing hole 11a. .

The first hole 33c is formed in series with the oil chamber 12 from the axial center of the sleeve 33, the second hole 33d having a larger diameter than the first hole 33c, and the third hole having a larger diameter than the second hole 33d. 33e and the third hole 33e are the fourth hole 33f having a large diameter.

A second valve seat 33g for seating or disengaging the second valve body 35 is formed at a boundary portion between the second hole 33d and the third hole 33e. The second valve seat 33g is formed so as to be swelled from the sleeve 33 in the valve opening direction (the right direction in FIG. 3), and is not in the portion other than the second valve seat 33g of the sleeve 33 and the second valve body 35. A gap is formed between them.

The first valve body 34 has a sliding portion 34a that slides along the first hole 33c of the sleeve 33, and a valve body portion 34b that is formed to have a larger diameter than the sliding portion 34a and that opens and closes the first valve seat 35a. The boundary portion between the sliding portion 34a and the valve body portion 34b is formed flat in the radial direction of the first valve body 34 so as to block the flow of the compressed air while resting on the first valve seat 35a, and from the first valve seat. The seat portion 34c is 35a away from the seat to allow the flow of compressed air. In the valve body portion 34b, a first reduced diameter portion 34d having an outer diameter smaller than that of the valve body portion 34b and a second reduced diameter portion 34e having a smaller outer diameter than the first reduced diameter portion 34d are sequentially formed on the side opposite to the sliding portion 34a.

The second valve body 35 has a valve body portion 35b that is annularly provided on the outer circumference of the sliding portion 34a of the first valve body 34, and a valve body portion 35b that is coupled to the valve body portion 35b and that extends in the valve opening direction and is provided in the first valve. The annular extending portion 35c of the outer periphery of the valve body portion 34b of the body 34.

As shown in FIG. 4A, the valve body portion 35b is slidably attached to the outer circumference of the sliding portion 34a of the first valve body 34, and the outer circumference is screwed to the inner circumference of the extending portion 35c (FIG. 3). A notch-like connecting passage 35d is formed along the sliding portion 34a of the first valve body 34 on the inner circumference of the valve body portion 35b. The connection passage 35d is provided at three locations in the circumferential direction of the valve body portion 35b, and is formed so as to extend from the end portion in the valve opening direction of the valve body portion 35b to the end portion in the valve closing direction (FIG. 3).

A first valve seat 35a for the valve body portion 34b of the first valve body 34 to be seated and seated is formed at an end portion of the valve body portion 35b in the valve opening direction. In the valve closing portion end portion of the valve body portion 35b, a second valve seat 33g which is formed to be raised from the sleeve 33 is formed flat in the radial direction of the second valve body 35. On the other hand, the seat portion 35e that blocks the flow of the compressed air and is separated from the second valve seat 33g to allow the flow of the compressed air.

The extended portion 35c is formed such that the inner circumference and the valve body portion 34b of the first valve body 34 have a predetermined gap, and the outer circumference and the third hole 33e have a predetermined gap. At the front end of the extended portion 35c, an engaging portion 35f formed to have a reduced inner diameter is provided. The extended portion 35c and the engaging portion 35f constitute one of the second valve bodies.

The engaging portion 35f has an inner diameter smaller than the outer diameter of the valve body portion 34b of the first valve body 34 and larger than the outer diameter of the first reduced diameter portion 34d. Further, the engagement portion 35f and the valve body portion 34b of the first valve body 34 are positioned at a predetermined distance in the axial direction (the horizontal direction in FIG. 3) when the first valve body 34 is seated on the first valve seat 35a. Separation. As a result, when the first valve body 34 is opened and then moved in the valve opening direction at a predetermined distance, the first valve body 34 is engaged with the second valve body 35 and integrally moved in the valve opening direction.

The extending portion 35c is further formed in the through hole 35g that penetrates the extended portion 35c in the radial direction. The through hole 35g that is a connecting passage defines a flow path for air on the inner peripheral side and the outer peripheral side of the extending portion 35c after the first valve body 34 is opened.

The fourth hole 33f of the sleeve 33 is press-fitted to the closing member 41 having a through passage (not shown) in the axial center. The closing member 41 is in close contact with the boundary portion of the third hole 33e and the fourth hole 33f to close the air chamber in the sleeve 33. The communication passage 9 that communicates with the compressor 7 is connected to the through passage of the closing member 41 of the air supply valve 31, and the air spring passage 6 is connected to the through passage of the closing member 41 of the exhaust valve 32. Further, in the case where the closing member 41 is not provided with a through passage, the communication passage 9 connected to the compressor 7 may be connected to the high pressure port 47 of the air supply valve 31, and the air spring passage 6 and the exhaust valve 32 may be connected. The high voltage interface 47 is connected.

Between the blocking member 41 and the valve body portion 34b of the first valve body 34, in a compressed state In the state, the coil spring 42 of the first valve body 34 is biased in the valve closing direction. The coil spring 42 is biased by a spring receiving member 43 that is fitted to the outer circumference of the second reduced diameter portion 34e of the valve body portion 34b of the first valve body 34, and the first valve body 34 is biased.

As shown in FIG. 4B, the spring receiving member 43 is in close contact with the second reduced diameter portion 34e of the first valve body 34, and the outer periphery is slidably connected to the inner wall of the third hole 33e at three locations in the circumferential direction. A portion other than the sliding portion that is in contact with the third hole 33e on the outer circumference of the spring receiving member 43 has a gap between the inner wall of the third hole 33e and the air passing through the sliding of the first valve body 34. .

In this manner, the spring receiving member 43 is fixed to the first valve body 34 so as to be press-fitted to the inner wall of the third hole 33e, and the second valve body 35 is slidably welded to the sliding portion 34a of the first valve body 34. Therefore, the first valve body 34 and the second valve body 35 are slidable in the axial direction and are restricted from moving in the radial direction.

A part of the sliding portion 34a of the first valve body 34 protrudes into the oil chamber 12. When the seat portion 34c is seated on the first valve seat 35a, the front end portion and the operating arm 22 have a predetermined gap and are opposed to each other. When the actuator arm 22 is rotated from the neutral position by a predetermined angle or more, the actuator arm 22 abuts against the front end portion of the sliding portion 34a. The first valve body 34 moves in accordance with the rotation of the writing arm 22 against the elastic pressure of the coil spring 42, and the seat portion 34c is separated from the first valve seat 35a, thereby opening the valve. When the first valve body 34 is opened, the second valve body 35 is moved by a predetermined distance in the valve opening direction, and the engagement portion 35f is engaged with the first valve body 34 and moved together with the first valve body 34. The seat portion 35e is separated from the second valve seat 33g to open the valve.

In this manner, the horizontal valve 100 has a predetermined gap between the actuator 22 and the air supply valve 31 and the exhaust valve 32 in order to provide a dead zone in which the compressed air is prohibited from being supplied to the air spring 3, even if it is actuated. The arm 22 is rotated from the neutral position, and the air valve 31 and the exhaust valve 32 are also Will not open the valve immediately. Thereby, the rotation of the actuator arm 22 at a predetermined angle is prohibited, and since the compressed air can be prohibited from being supplied to the air spring 3, the hunting of the air supply valve 31 and the exhaust valve 32 can be prevented. The dead zone of the air supply valve 31 and the exhaust valve 32 is set by adjusting the thickness or the number of the washers 13.

In the sleeve 33, a first air chamber 44 that constantly communicates with the exhaust passage 8 and a first valve body 34 and a second valve body 35 are separated from the first air chamber 44 and pass through the air spring passage 6 . A second air chamber 45 that is in constant communication with the air spring 3. Further, the second air chamber 45 of the air supply valve 31 is constantly in communication with the compressor 7 through the communication path 9.

Since the second valve body 35 is provided on the outer circumference of the sliding portion 34a of the first valve body 34, the pressure receiving area of the second valve body 35 is larger than the pressure receiving area of the first valve body 34. Therefore, when the first valve body 34 and the second valve body 35 are simultaneously closed, the force of the second valve body 35 in the valve closing direction due to the pressure difference between the first air chamber 44 and the second air chamber 45 is larger than The first valve body 34 receives a force in the valve closing direction due to the pressure difference between the first air chamber 44 and the second air chamber 45.

The sleeve 33 is formed with a low pressure port 46 that communicates with the first air chamber 44 and a high pressure port 47 that communicates with the second air chamber 45 so as to penetrate the inner and outer peripheral surfaces of the sleeve 33. The low pressure port 46 is in constant communication with the first annular passage 48 formed in the valve casing 11. The high pressure port 47 is in constant communication with the second annular passage 49 formed in the valve casing 11.

The first annular passage 48 of the air supply valve 31 and the second annular passage 49 of the exhaust valve 32 communicate with each other through the communication passage 10 formed in the valve casing 11. That is, the low pressure port 46 of the air supply valve 31 and the high pressure port 47 of the exhaust valve 32 are communicated through the communication passage 10. A check valve (not shown) that allows only compressed air to flow from the low pressure port 46 of the air supply valve 31 to the high pressure port 47 of the exhaust valve 32 is provided in the middle of the communication path 10. In addition, the low pressure port 46 of the exhaust valve 32 is open. The first annular passage 48 passes through the exhaust passage 8 .

Next, the operation of the horizontal valve 100 will be described.

When the load of the vehicle body is reduced and the air spring 3 is extended, the rocker 4 is pressed downward from the neutral position corresponding to the relative displacement of the vehicle body 1 with respect to the carriage 2 (Fig. 1), and accordingly, the buffer spring 23 is deformed. The restoring force of the buffer spring 23 is transmitted to the actuator 22, and the actuator 22 is rotated from the neutral position in the direction of the arrow B in FIG.

When the actuator 22 has been rotated by a predetermined angle or more, the actuator 22 presses the first valve body 34 of the exhaust valve 32. At this time, the first valve body 34 counteracts the force calculated by multiplying the pressure difference between the first gas chamber 44 and the second gas chamber 45 by the pressure receiving area that receives the pressure difference, and the spring force of the coil spring 42. Move and open the valve. Further, in this case, the valve body is only the first valve body 34. Therefore, the pressure receiving area is only the pressure receiving area of the first valve body 34 and does not include the pressure receiving area of the second valve body 35.

As shown in FIG. 5, when the first valve body 34 is opened, the first air chamber 44 and the second air chamber 45 of the exhaust valve 32 are transmitted through the connecting passage 35d of the second valve body 35 and the through hole of the extending portion 35c. 35g and connected. Further, when the first valve body 34 is opened and then moved in the valve opening direction at a predetermined distance, the engaging portion 35f is engaged with the first valve body 34.

At this time, since the first gas chamber 44 communicates with the second gas chamber 45, the pressure difference between the first gas chamber 44 and the second gas chamber 45 is lowered. Further, a gap is formed between the end portion of the second valve body 35 in the valve closing direction and the sleeve 33. Therefore, the force generated by the pressure difference between the first air chamber 44 and the second air chamber 45 is hardly generated. The second valve body 35 functions.

As shown in FIG. 6, when the first valve body 34 moves further in the valve opening direction, the second valve body 35 moves in the valve opening direction together with the first valve body 34. Thereby, the first gas chamber 44 and the first The second gas chamber 45 communicates between the second valve body 35 and the sleeve 33.

At this time, although the first valve body 34 moves the second valve body 35 through the engaging portion 35f, the force generated by the pressure difference between the first air chamber 44 and the second air chamber 45 is almost the same as described above. Since the second valve body 35 acts, there is almost no case where the pressing force required for the actuator 22 is increased in order to open the second valve body 35. In other words, when the first valve body 34 and the second valve body 35 are simultaneously opened, the second valve body 35 is received in the valve closing direction due to the pressure difference between the first gas chamber 44 and the second gas chamber 45. The force is eliminated as the first valve body 34 is opened.

Thereby, the compressed air of the air spring 3 is discharged to the atmosphere through the second air chamber 45 of the exhaust valve 32, the first air chamber 44, the low pressure port 46, and the exhaust passage 8. In addition, the high pressure port 47 of the exhaust valve 32 communicates with the contact passage 10 through the low pressure port 46 of the air supply valve 31. However, the compressed air of the air spring 3 does not pass through the check valve provided in the contact passage 10. The case where the side of the gas valve 31 flows in.

On the other hand, in the case where the load of the vehicle body increases and the air spring 3 is deflected, the rocker 4 is pressed upward from the neutral position corresponding to the relative displacement of the vehicle body 1 with respect to the carriage 2 (Fig. 1), and accordingly, the buffer spring 23 Deformation. The restoring force of the buffer spring 23 is transmitted to the actuator 22, and the actuator 22 is rotated from the neutral position in the direction of the arrow A in FIG.

When the actuator arm 22 has been rotated by a predetermined angle or more, the actuator arm 22 presses the first valve body 34 of the air supply valve 31. At this time, the first valve body 34 counteracts the force calculated by multiplying the pressure difference between the first gas chamber 44 and the second gas chamber 45 by the pressure receiving area that receives the pressure difference, and the spring force of the coil spring 42. Move and open the valve. Further, in this case, the valve body is only the first valve body 34. Therefore, the pressure receiving area is only the pressure receiving area of the first valve body 34 and does not include the pressure receiving area of the second valve body 35.

When the first valve body 34 is opened, the first air chamber 44 and the second air chamber 45 of the air supply valve 31 communicate with each other through the connection passage 35d of the second valve body 35 and the through hole 35g of the extension portion 35c. Further, when the first valve body 34 is opened and then moved in the valve opening direction at a predetermined distance, the engaging portion 35f is engaged with the first valve body 34.

At this time, since the first gas chamber 44 communicates with the second gas chamber 45, the pressure difference between the first gas chamber 44 and the second gas chamber 45 is lowered. Further, since a gap is formed between the end portion of the second valve body 35 in the valve closing direction and the sleeve 33, the force generated by the pressure difference between the first air chamber 44 and the second air chamber 45 is hardly generated. It will act on the second valve body 35.

When the first valve body 34 moves further in the valve opening direction, the second valve body 35 moves in the valve opening direction together with the first valve body 34. Thereby, the first gas chamber 44 and the second gas chamber 45 are communicated between the second valve body 35 and the sleeve 33.

At this time, although the first valve body 34 passes through the engaging portion 35f to move the second valve body 35, as described above, the force generated by the pressure difference between the first air chamber 44 and the second air chamber 45 hardly occurs. Since the second valve body 35 acts, the pressing force required for the actuator 22 is hardly increased in order to open the second valve body 35. In other words, when the first valve body 34 and the second valve body 35 are simultaneously closed, the second valve body 35 is received in the valve closing direction by the pressure difference between the first air chamber 44 and the second air chamber 45. The force is eliminated as the first valve body 34 is opened.

Thereby, the compressed air of the air spring 3 presses the check valve of the communication passage 10 from the second air chamber 45, the first air chamber 44, and the low pressure port 46 of the air supply valve 31, and passes through the high pressure port 47 of the exhaust valve 32. The second air chamber 45 is supplied to the air spring 3.

Once the compressed air of the compressor 7 is supplied to the air spring 3 through the air supply valve 31 and the air spring 3 is restored to a certain height, the rocker 4 is returned to the neutral position and the boom 22 is also moved. The neutral position returns. Thereby, the first valve body 34 of the air supply valve 31 is seated on the first valve seat 35a by the spring pressure of the coil spring 42, and the second valve body 35 is seated on the second valve seat 33g to close the air valve 31. The valve blocks the supply of compressed air.

According to the above embodiment, the effects shown below are exhibited.

When the first valve body 34 is opened by the rotation of the writing arm 22, air flows through the through hole 35g and the connecting passage 35d, so that the pressure difference between the first air chamber 44 and the second air chamber 45 is lowered. The valve body 35 is opened together with the first valve body 34 through the engaging portion 35f. Thereby, the actuator arm 22 can open the second valve body 35 having a larger pressure receiving area than the first valve body 34 by only the force of pressing the first valve body 34 in the valve opening direction. According to this, it is possible to secure a large flow path area without increasing the size of the buffer spring 23 that imparts rotational force to the actuator 22 .

Further, the second valve seat 33g is formed to bulge from the sleeve 33 in the valve opening direction, and has a flow path between the inner circumference of the sleeve and the outer circumference of the second valve body 35. Thereby, the air pressure can be guided to the gap between the end portion side in the valve closing direction of the second valve body 53 and the second valve seat 33g formed in the sleeve 33 by the flow path. By the air pressure, the second valve body 35 is often pressed in the valve opening direction. Therefore, after the first valve body 34 is opened by the rotation of the writing arm 22, the first valve body 34 passes through the engaging portion 35f. When the second valve body 35 is moved in the valve opening direction, the pressing force required for the boom 22 can be suppressed from increasing. According to this, since the second valve body 35 can be opened more reliably, it is possible to secure a large flow path area without increasing the size of the buffer spring 23.

Further, since the through hole 35g is formed in the extended portion 35c, the flow path area of the passage that connects the first gas chamber 44 and the second gas chamber 45 can be increased when the first valve body 34 is opened, and The pressure difference between the first gas chamber 44 and the second gas chamber 45 is rapidly lowered. Further, even if the first valve body 34 is moved by a predetermined distance after opening the valve and is engaged with the engaging portion 35f, the first air chamber can be held. Since the 44 is in communication with the second air chamber 45, the second valve body 35 can be more reliably opened.

Although the embodiment of the present invention has been described above, the above embodiment is merely one of the application examples of the present invention, and the technical scope of the present invention is not limited to the specific configuration of the above embodiment.

For example, in the above-described embodiment, the cross section of the connecting passage 35d is formed in a semicircular shape as shown in FIG. 4A, but the connecting passage 55d may be formed in an elliptical shape as shown in FIG. When the cross-sectional area of the connecting passage 55d is increased, the pressure difference between the first air chamber 44 and the second air chamber 45 can be more quickly lowered when the first valve body 34 is opened.

Further, in the above-described embodiment, the first valve body 34 and the second valve body 35 are respectively provided in the air supply valve 31 and the exhaust valve 32. However, only the air supply valve 31 and the exhaust valve 32 may be provided. One of them has the first valve body 34 and the second valve body 35, and the other has only a single valve body.

3‧‧‧Air spring

6‧‧‧Air spring passage

7‧‧‧Compressor

8‧‧‧ exhaust passage

9‧‧‧Connected Road

10‧‧‧Contact Path

11‧‧‧Valve

12‧‧‧ oil room

13‧‧‧ Washer

20‧‧‧buffer spring section

21‧‧‧Axis

22‧‧‧Betting arm

23‧‧‧buffer spring

25‧‧‧ oil damper

31‧‧‧Air supply valve

32‧‧‧Exhaust valve

33‧‧‧ sleeve

34‧‧‧1st valve body

35‧‧‧2nd valve body

41‧‧‧ occlusion components

42‧‧‧Helical spring

43‧‧‧Spring bearing member

44‧‧‧1st air chamber

45‧‧‧2nd gas chamber

46‧‧‧Low-voltage interface

47‧‧‧High voltage interface

48‧‧‧1st circular path

49‧‧‧2nd circular path

100‧‧‧ horizontal valve

11a‧‧‧ valve receiving hole

11b‧‧‧Mask thread

33a‧‧‧ Male thread department

33b‧‧‧锷

33c‧‧‧1 hole

33d‧‧‧2nd hole

33e‧‧‧3rd hole

33f‧‧‧4th hole

34a‧‧‧Sliding section

34b‧‧‧ Body Department

35a‧‧‧1st seat

Claims (4)

A horizontal valve is configured to adjust a height of an air spring disposed between a body of a railway vehicle and a trolley, and is characterized in that: a rocker is provided to rotate relative to a relative displacement of the vehicle body relative to the trolley; Actuating the arm, which is rotated by the restoring force of the buffer spring deformed by the rotation of the rocker; and connecting the valve by the rotation of the actuator arm against the air pressure and opening the valve, and An air spring passage communicating with the air spring is connected to a compressed air source or an exhaust passage; the connecting valve has a first valve body that presses the actuator arm and moves in a valve opening direction as the actuator arm rotates; The second valve body has a first valve seat on which the first valve body is seated and seated, and a sleeve in which the first valve body and the second valve body are disposed, and the second valve body is provided a second valve seat having a ring-shaped seat and a seated ring; the biasing member is disposed in the sleeve, and biases the first valve body toward the first valve seat; and the elastic receiving portion is Provided in the first valve body for receiving the elastic pressure of the elastic member; and the engaging portion When the first valve body is moved by a predetermined distance after the first valve body is opened, the second valve body is engaged with the first valve body to move the second valve body together with the first valve body in a valve opening direction; The first valve body is slidably held by the second valve body; the elastic pressure receiving portion is slidably held by the sleeve; The pressure receiving area of the second valve body is larger than the pressure receiving area of the first valve body. The horizontal valve according to claim 1, wherein the second valve seat is formed by bulging from the sleeve in a valve opening direction, and has a flow path on an inner circumference of the sleeve and an outer circumference of the second valve body. . The horizontal valve according to claim 1, wherein the second valve body further has a through hole formed between the first valve seat and the engagement portion and penetrating the second valve body in the radial direction. The horizontal valve of claim 1, wherein the connecting valve is opened by rotating the actuator arm from a neutral position in a direction by a predetermined angle or more, and the compressed air source is connected to the air spring passage. The air supply valve and the exhaust valve that is opened by rotating the predetermined arm from the neutral position in the other direction by a predetermined angle or more and connected to the air passage in the air spring passage are configured.