JP4728182B2 - Body posture control device - Google Patents

Description

  The present invention relates to a vehicle body posture control device that controls a posture change of a railway vehicle.

  When the railway vehicle travels in a curved section, a centrifugal force directed to the opposite side from the center of curvature of the curved section acts on the railway vehicle. This centrifugal force increases as the traveling speed of the vehicle increases. Therefore, in the railroad track, a height difference called Kant is provided on the inner rail on the opposite side of the center of curvature and the outer rail on the opposite side to alleviate the centrifugal force, thereby improving the speed of the railcar during curve driving. .

However, the cant amount (the difference in height of each rail) cannot be changed once set. In a line section where a rail vehicle with a different traveling speed travels, the higher the rail vehicle travels at a higher speed, the greater the cant amount. There is a problem in that the excess centrifugal force acts on the railway vehicle and the ride comfort deteriorates.

  Therefore, in recent years, in order to reduce the excess centrifugal force due to the shortage of the cant amount, a railway vehicle is curved so that a control device that controls the posture of the vehicle body using a gas spring provided between the carriage and the vehicle body is mounted. When traveling in a section, the vehicle body is tilted toward the center of curvature with respect to the carriage to achieve high-speed traveling in a curved section (see, for example, Patent Documents 1, 2, and 3).

Specifically, the control device supplies gas to one of the gas springs provided on the left and right with respect to the vehicle traveling direction between the carriage and the vehicle body according to the turning direction of the railway vehicle, Lifts the opposite side to tilt the vehicle body toward the center of curvature relative to the carriage.
JP 7-81558 A JP-A-11-78875 Japanese Patent Laid-Open No. 2005-1520

  However, the above control device may point out that there are the following adverse effects.

In other words, in the conventional control device, when the railway vehicle runs off the curved section and travels in the straight section, the pressure of the gas spring that lifts the vehicle body is reduced, and the vehicle body is returned to the carriage horizontally. Although we are trying to control the posture with only the gas spring, when the vehicle body returns from the inclined state to the horizontal state, the phenomenon that the vehicle is tilted to the opposite side beyond the horizontal state, the so-called change or There is a concern that the hunting that causes the vehicle body to continue to swing in the left-right direction (rolling) is caused and the ride comfort in the vehicle is deteriorated.

That is, in the conventional control system, because it attempts to control the body attitude only by the gas spring, poor damping effect on rolling and pitching is from being to lead to deterioration of the ride comfort in the vehicle.

  Accordingly, the present invention has been developed to improve the above-described problems, and an object of the present invention is to provide a vehicle body attitude control device that is optimal for railway vehicle attitude control.

In order to achieve the above-described object, the vehicle body posture control device in the problem solving means of the present invention includes a damping valve that provides resistance to the flow of liquid during expansion and contraction, a bypass passage that bypasses the damping valve, and a middle of each bypass passage. And has two or more hydraulic dampers interposed between the bogie and the vehicle body of the railway vehicle, and the on-off valve in any one hydraulic damper includes the hydraulic damper When the internal pressure exceeds a predetermined amount of pressure in any other hydraulic damper, the bypass passage is opened.

  According to the attitude control device of the present invention, it is possible to generate a smaller damping force as the stroke speed difference of the hydraulic damper becomes larger, and it is possible to effectively prevent rolling, pitching and vertical vibration in the body of a railway vehicle. Therefore, the ride comfort in the vehicle can be improved.

  In addition, the vehicle body tilt control operation during curved section travel is not hindered by the arrangement on the railroad vehicle, and the rolling of the vehicle body can be prevented from rolling back, hunting, and excessively returning the vehicle body. Optimal for control.

  FIG. 1 is a plan view of a railway vehicle. FIG. 2 is a side view of the railway vehicle. FIG. 3 is a diagram conceptually illustrating the vehicle body attitude control device according to the embodiment. FIG. 4 is a diagram showing a specific configuration of an integrated on-off valve. FIG. 5 is a diagram showing another specific configuration of the integrated on-off valve. FIG. 6 is a diagram illustrating an example of the arrangement of the hydraulic damper with respect to the railway vehicle in the vehicle body attitude control device. FIG. 7 is a diagram showing an example of the arrangement of the hydraulic damper with respect to the railway vehicle in the vehicle body attitude control device. FIG. 8 is a diagram showing an example of the arrangement of the hydraulic damper with respect to the railway vehicle in the vehicle body attitude control device. FIG. 9 is a diagram showing an example of the arrangement of the hydraulic damper with respect to the railway vehicle in the vehicle body attitude control device. FIG. 10 is a diagram showing an example of the arrangement of the hydraulic damper with respect to the railway vehicle in the vehicle body attitude control device. FIG. 11 is a diagram illustrating an example of the arrangement of the hydraulic damper with respect to the railway vehicle in the vehicle body attitude control device. FIG. 12 is a diagram illustrating an example of the arrangement of the hydraulic damper with respect to the railway vehicle in the vehicle body attitude control device. FIG. 13 is a diagram conceptually showing a vehicle body attitude control device in another embodiment.

  As shown in FIG. 1, a railway vehicle V to which the vehicle body posture control device 1 is applied includes a vehicle body B and a carriage that is disposed forward and backward with respect to the traveling direction of the vehicle body B and supports the vehicle body B via a gas spring A. The vehicle body B is configured to be rotatable around a point a with respect to the carts T1 and T2, respectively. Further, as shown in FIG. 2, gas springs A are interposed between the vehicle body B and each of the carts T1 (T2) on the left and right with respect to the vehicle traveling direction, and gas is supplied to one of the left and right gas springs A. By supplying the vehicle body B, the vehicle body B can be inclined to one side with respect to the carriage T1 (T2) as indicated by a broken line in FIG.

On the other hand, as shown in FIGS. 2 and 3, the vehicle body attitude control device 1 is disposed between the carriage T <b> 1 (T <b> 2) of the railway vehicle V and the vehicle body B so as to be arranged on the left and right with respect to the vehicle traveling direction. Hydraulic dampers 2R and 2L are provided. The hydraulic dampers 2R and 2L respectively have damping valves 3R and 3L that give resistance to the flow of liquid during expansion and contraction, bypass passages 4R and 4L that bypass the damping valves 3R and 3L, and bypass passages 4R and 4L, respectively. The on-off valves 5R and 5L provided in the middle of the

  Hereinafter, the vehicle body attitude control device 1 will be described in detail. The hydraulic dampers 2R and 2L are both slidably inserted into the cylinder 10, and the cylinder 10 is slidably inserted into the rod side chamber R and the piston side chamber P. A piston 11 that is partitioned into a cylinder 10 and is connected to the piston 11 at one end, a damping passage 14 that connects the rod side chamber R to the tank 13, and a piston 11 that is provided in the piston 11 from the rod side chamber R to the piston. A check valve 15 that blocks the flow of liquid toward the side chamber P, a suction passage 16 that connects the piston side chamber P and the tank 13, and a liquid flow that is provided in the middle of the suction passage 16 toward the tank 13 from the piston side chamber P In addition, the hydraulic damper 2R is provided with a check valve 17 from the rod side chamber R in the middle of the damping passage 14. In the hydraulic damper 2L, a damping valve 3R that provides resistance to the flow of liquid toward 13 and blocks the flow of liquid from the tank 13 toward the rod side chamber R is provided in the middle of the damping passage 14 from the rod side chamber R. A damping valve 3L that provides resistance to the flow of liquid toward the tank 13 and blocks the flow of liquid from the tank 13 toward the rod side chamber R is provided.

  Furthermore, the rod cross-sectional area when the rod 12 is cut right side in FIG. 3 is set to be a half of the piston cross-sectional area when the piston 11 is cut right side in FIG. .

  For example, when the hydraulic dampers 2R and 2L extend, the volume of the piston side chamber P increases, and the check valve 15 prevents the liquid from moving from the rod side chamber R to the piston side chamber P. Is supplied from the tank 13 via the check valve 17 and the volume of the other rod side chamber R is reduced by the volume of the rod 12 entering the cylinder 10. Since the valve 15 prevents the liquid from moving from the rod side chamber R to the piston side chamber P, the liquid commensurate with the volume reduction is discharged from the rod side chamber R to the outside of the cylinder 10.

  On the contrary, when the hydraulic dampers 2R and 2L contract, the volume of the piston side chamber P decreases and the movement of the liquid to the tank 13 is prevented by the check valve 17, so that the liquid commensurate with the volume reduction is retained in the piston side chamber. It moves from P to the rod side chamber R via the check valve 15. Although the volume of the other rod side chamber R increases, the increase amount is smaller than the volume decrease amount of the piston side chamber P by the volume amount of the rod 12 that moves out of the cylinder 10, so that the liquid moving from the piston side chamber P to the rod side chamber R The volume of the rod 12 withdrawing out of the cylinder 10 becomes excessive in the cylinder 10, and the liquid is discharged from the rod side chamber R to the outside of the cylinder 10.

  That is, the hydraulic pressure dampers 2R and 2L always discharge liquid from the rod side chamber R to the outside of the cylinder 10 when expanding and contracting, and the flow of the liquid in the cylinder 10 is controlled by the check valves 15 and 17. The hydraulic dampers 2R and 2L are both so-called single rod uniflow type hydraulic dampers.

  Also, since the hydraulic dampers 2R and 2L have a rod cross-sectional area set to one half of the piston cross-sectional area, the rod side chamber can be used as long as the displacement of the piston 11 relative to the cylinder 10 is the same during expansion and contraction. The amount of liquid discharged from the cylinder 10 from R becomes equal.

Subsequently, the rod-side chamber R of the hydraulic damper 2R is connected to the tank 13 via a bypass passage 4R that bypasses the damping valve 3R, and an opening / closing valve 5R is provided in the middle of the bypass passage 4R, and the other hydraulic damper. The 2L rod-side chamber R is also connected to the tank 13 via a bypass passage 4L that bypasses the damping valve 3L, and an on-off valve 5L is provided in the middle of the bypass passage 4L. These on-off valves 5R and 5L are provided in a center block 20 which is a housing arranged separately from the center of the hydraulic dampers 2R and 2L.

The tank 13 is provided with an outer cylinder 18 that covers the outer periphery of the cylinder 10 of the hydraulic dampers 2R, 2L, and is formed between the cylinder 10 and the outer cylinder 18, and each of the hydraulic dampers 2R, 2L Since the tank 13 is provided, the hydraulic dampers 2R, 2L can hold the damping valves 3R, 3L, and the hydraulic dampers 2R, 2L and the center block 20 are connected. Since the piping is only the bypass passages 4R and 4L, the piping in the vehicle body attitude control device 1 is simplified, and the mountability to the railway vehicle V is improved. Although each of the hydraulic dampers 2R and 2L is provided with the tank 13, one tank 13 may be provided separately.

  Further, the hydraulic dampers 2R and 2L are set to a double cylinder type having the tank 13 on the outer peripheral side, and a configuration is adopted in which the liquid discharged from the center block 20 having the on-off valves 5R and 5L is returned to the tank 13. Therefore, when connecting the hydraulic dampers 2R, 2L and the center block 20, there is no need to bleed air, it is only necessary to inject a fixed amount of liquid, and the manufacture of the vehicle body attitude control device 1 is facilitated.

  Further, even when air in the hydraulic dampers 2R and 2L and the center block 20 is mixed, by expanding and contracting the hydraulic dampers 2R and 2L, the air mixed liquid circulates in the tank 13, The air can be removed, the handling is easy, and the function can be restored.

Returning, the on-off valve 5R in the hydraulic damper 2R is an on-off valve that opens and closes using the pressure in the rod side chamber R of the hydraulic damper 2R and the pressure in the rod side chamber R of the other hydraulic damper 2L as pilot pressures. When the pressure in the rod side chamber R of the hydraulic damper 2R exceeds the pressure in the rod side chamber R of the other hydraulic damper 2L by a predetermined amount, the valve is opened to open the bypass passage 4R. The on-off valve 5L is also an on-off valve that opens and closes using the pressure in the rod side chamber R of the hydraulic damper 2L and the pressure in the rod side chamber R of the counterpart hydraulic damper 2R as a pilot pressure, and the rod of the hydraulic damper 2L When the pressure in the side chamber R exceeds the pressure in the rod side chamber R of the other hydraulic damper 2R by a predetermined amount, the valve opening operation is performed to open the bypass passage 4L .

Specifically, the on-off valve 5R includes a valve body 21 and a spring 22 that urges the valve body 21 in the direction to close the bypass passage 4R, and the pressure in the rod side chamber R of the hydraulic damper 2R is As a pilot pressure in a direction against the urging force of the spring 22, the pressure in the rod side chamber R of the other hydraulic damper 2 </ b> L is applied to the valve body 21 as a pilot pressure in the same direction as the urging force of the spring 22. It has become. The on-off valve 5L has a substantially similar configuration, but in the on-off valve 5L, the pressure in the rod side chamber R of the hydraulic damper 2R is set as the pilot pressure in the same direction as the urging force of the spring 22, and the other The pressure in the rod side chamber R of the hydraulic damper 2L is applied to the valve body 21 as a pilot pressure in a direction against the urging force of the spring 22.

Therefore, when the pressure in the rod side chamber R of the hydraulic damper 2R exceeds the pressure in the rod side chamber R of the other hydraulic damper 2L, the on-off valve 5R compresses the spring 22 to retract the valve body 21. , now opens the bypass passage 4R, the predetermined amount is Kesse by setting the biasing force of the spring 22. The on-off valve 5L is set similarly.

In the case of this embodiment, the predetermined amount is as small as possible. Basically, the pressure in the rod side chamber R of the hydraulic damper 2R is the pressure in the rod side chamber R of the other hydraulic damper 2L. When the difference is exceeded, the on-off valve 5R is set to open the bypass passage 4R, and even in the other on-off valve 5L, the pressure in the rod side chamber R of the other hydraulic damper 2L is the hydraulic damper. When the pressure exceeds the pressure in the rod side chamber R of 2R, the bypass passage 4L is set to be opened.

Therefore, in the hydraulic damper 2R, when the hydraulic damper 2R expands and contracts and the liquid is discharged from the rod side chamber R to the outside of the cylinder 10, the open / close valve 5R opens the bypass passage 4R. When the discharged liquid bypasses the damping valve 3R and is guided to the tank 13 and the hydraulic damper 2R generates almost no damping force, on the other hand, the on-off valve 5R closes the bypass passage 4R. Since the discharged liquid passes through the damping valve 3R and is guided to the tank 13, the hydraulic damper 2R generates a damping force.

Similarly to the hydraulic damper 2R, when the other hydraulic damper 2L expands and contracts, when the on-off valve 5L opens the bypass passage 4L, the discharged liquid bypasses the damping valve 3L and bypasses the tank 13 When the hydraulic damper 2L generates almost no damping force and the on-off valve 5L closes the bypass passage 4L, the discharged liquid passes through the damping valve 3L and passes through the tank 13. Therefore, the hydraulic damper 2L generates a damping force.

  Each of the damping valves 3R and 3L is set to generate the same damping force with respect to the stroke speed when the hydraulic dampers 2R and 2L are expanded and contracted.

Further, the configuration of the on-off valves 5R and 5L housed in the center block 20 can be integrally configured using a spool 33 as shown in FIG.

More specifically, the on-off valves 5R and 5L include a center block 20 that is a hollow housing, a spool 33 that defines two chambers 31 and 32 in the center block 20, and one chamber 31 that bypasses the hydraulic damper 2R. A port 20a connected to the passage 4R, a port 20b connecting the other chamber 32 to the bypass passage 4L of the hydraulic damper 2L, a tank port 20c connecting the inside of the center block 20 to the tank 13 via the bypass passage, and a spool And springs 34 and 35 for biasing 33 from both ends and positioning it at the neutral position.

  Further, the spool 33 is maintained in a neutral position in a state where there is no difference between the pressures in the chambers 31 and 32, and the outer periphery of the spool 33 is opposed to the tank port 20c. 32 also does not communicate with the tank port 20c.

Therefore, when the pressure in the rod side chamber R of the hydraulic damper 2R exceeds the pressure in the rod side chamber R of the other hydraulic damper 2L by a predetermined amount, the spool 33 moves to the left in FIG. communicates with an open bypass passage 4R, conversely, when the pressure in the rod side chamber R of the hydraulic damper 2L exceeds a predetermined amount of pressure in the rod side chamber R of the hydraulic damper 2R, spool 33 is the right side in FIG. 4 The chamber 32 is communicated with the tank port 20c and the bypass passage 4L is opened, and the same operation as the on-off valves 5R and 5L is realized. With the above configuration, the on-off valves 5R and 5L can be integrated rather than separately, and the manufacturing cost of the on-off valves 5R and 5L is reduced. In this case, the setting of the predetermined amount is determined by the urging force of the springs 34 and 35 and the amount of movement from the neutral position of the spool 33 for opening the bypass passages 4R and 4L.

  Further, as shown in FIG. 5, the damping valves 3 </ b> R and 3 </ b> L may be provided in the spool 40. The on-off valve shown in FIG. 5 differs from the on-off valve shown in FIG. 4 only in the structure of the spool 40.

  The spool 40 will be described in detail. The spool 40 is provided with a small diameter portion 41 with a small diameter at the center, and both outer circumferences of the large diameter are in sliding contact with the inner circumference of the center block 20 via the annular seals 42, respectively. ing.

  A damping passage 43 is provided from the end of the spool 40 facing one chamber 31 to the outer periphery of the small diameter portion 41, and a damping valve 3 </ b> R is provided in the middle of the damping passage 43. Further, a damping passage 44 is provided from the end of the spool 40 facing the other chamber 32 to the outer periphery of the small diameter portion 41, and a damping valve 3 </ b> L is provided in the middle of the damping passage 44.

Therefore, in the on-off valve shown in FIG. 5, when the pressure in the rod side chamber R of the hydraulic damper 2R exceeds the pressure in the rod side chamber R of the other hydraulic damper 2L by a predetermined amount, the spool 40 moves to the left in FIG. The chamber 31 moves to connect the tank port 20c to open the bypass passage 4R. Conversely, the pressure in the rod side chamber R of the hydraulic damper 2L exceeds the pressure in the rod side chamber R of the hydraulic damper 2R by a predetermined amount. Then, the spool 40 moves to the right side in FIG. 5 to connect the chamber 32 to the tank port 20c, and the bypass passage 4L is opened, and the same operation as that of the on-off valves 5R and 5L is realized.

In addition to this, when there is no difference between the pressure in the rod side chamber R of the hydraulic damper 2R and the pressure in the rod side chamber R of the other hydraulic damper 2L, the spool 40 maintains the neutral position. The liquid moving from the chamber 31 to the tank 13 passes through the attenuation passage 43 provided in the spool 40, and the liquid moving from the chamber 32 to the tank 13 passes through the attenuation passage 44 provided in the spool 40. Accordingly, the hydraulic dampers 2R and 2L expand and contract, and the liquid is discharged from the rod side chamber R to the outside of the cylinder 10, and the pressure in the rod side chamber R of the hydraulic damper 2R and the pressure in the rod side chamber R of the other hydraulic damper 2L are If there is no difference, the liquid discharged from the hydraulic damper 2R passes through the damping valve 3R and moves to the tank 13, and the liquid discharged from the hydraulic damper 2L passes through the damping valve 3L and moves to the tank 13. As a result, each of the hydraulic dampers 2R and 2L generates a damping force.

  That is, the on-off valve in FIG. 5 integrates not only the on-off valves 5R and 5L but also the damping passage and the damping valve. By configuring as shown in FIG. Thus, the manufacture of the vehicle body posture control device 1 can be simplified, the main parts of the vehicle body posture control device 1 can be replaced by replacing only the center block 20, and the maintenance work is facilitated.

  Further, since the damping valves 3R and 3L do not have to be provided in the hydraulic dampers 2R and 2L, the hydraulic dampers 2R and 2L can be made compact, and the mountability of the vehicle body attitude control device 1 to the rail vehicle V is improved. can do.

Now, the operation of the vehicle body posture control device 1 configured as described above will be described. If the hydraulic damper 2R on the right side in FIG. 3 expands or contracts and the hydraulic damper 2L on the left side in FIG. 3 does not expand or contract, the pressure in the rod side chamber R of the hydraulic damper 2R rises, and the other liquid Since the pressure in the rod side chamber R of the pressure damper 2L does not increase, the pressure in the rod side chamber R of the hydraulic damper 2R exceeds the pressure in the rod side chamber R of the other hydraulic damper 2L, and the on-off valve 5R is connected to the bypass passage 4R. On the other hand, the on-off valve 5L remains closed.

Therefore, the liquid discharged from the rod-side chamber R of the hydraulic damper 2R passes through the bypass passage 4R and moves to the tank 13, and in this state, the hydraulic damper 2R has a damping force even if it expands and contracts. It hardly occurs.

  Subsequently, when the hydraulic damper 2R on the right side in FIG. 3 and the hydraulic damper 2L on the left side in FIG. 3 expand and contract in the same phase or in opposite phase, the hydraulic damper 2R is discharged from the rod side chamber R of the hydraulic damper 2R, 2L. Since the amount of liquid is the same, there is no pressure difference between the pressure in the rod side chamber R of the hydraulic damper 2R and the pressure in the rod side chamber R of the other hydraulic damper 2L, and the on-off valves 5R and 5L are closed. Since the liquid discharged from the hydraulic dampers 2R and 2L passes through the damping valves 3R and 3L and moves to the tank 13, any of the hydraulic dampers 2R and 2L generates a damping force. .

Moreover, the stroke speed of the hydraulic damper 2L although stretchable than the stroke speed of the hydraulic damper 2R regardless of the hydraulic damper 2L and is in phase opposite the phase of the left side of the hydraulic damper 2R and Figure of right side in FIG. 3 3 In the slow state, the pressure in the rod side chamber R of the hydraulic damper 2R exceeds the pressure in the rod side chamber R of the other hydraulic damper 2L, and the on-off valve 5R opens the bypass passage 4R. 5L remains closed. In this case, since the predetermined amount is set to a small value, the pressure in the rod side chamber R of the hydraulic damper 2R is substantially the same as the pressure in the rod side chamber R of the other hydraulic damper 2L. The on-off valve 5R opens the bypass passage 4R until only a part of the liquid discharged from the rod side chamber R of the hydraulic damper 2R passes through the damping valve 3R. The generated damping force is smaller than the damping force generated when the hydraulic damper 2R and the hydraulic damper 2L expand and contract in the same phase or opposite phase. The generated damping force of the hydraulic damper 2L having a slow stroke speed is the same as the damping force generated when the hydraulic damper 2R and the hydraulic damper 2L are expanded or contracted in the same phase or in the opposite phase.

  That is, in the vehicle body attitude control device 1, when the stroke speeds of the hydraulic pressure dampers 2R and 2L are different, the generated damping force of the hydraulic pressure dampers 2R and 2L having the higher stroke speed becomes smaller, and one hydraulic damper 2R. , 2L expands and contracts, the hydraulic dampers 2R, 2L generate almost no damping force. When the hydraulic dampers 2R, 2L stroke at a constant speed, the hydraulic dampers 2R, 2L are large. A damping force will be generated.

  Then, the vehicle body attitude control device 1 operating in this way places the hydraulic damper 2R and the hydraulic damper 2L in the vehicle traveling direction between the carriage T1 (T2) of the railway vehicle V and the vehicle body B as shown in FIG. On the other hand, they are arranged on the left and right.

  For example, when the railway vehicle V is traveling in a curved section and the vehicle body B is inclined to the left side in FIG. 2 as shown by a broken line in order to reduce excess centrifugal force, the gas spring A on the left side in FIG. Also, gas is supplied to support the load increment due to the vehicle body tilt, and the original height of the left side of the vehicle body B is maintained.

  Then, the hydraulic damper 2L in the vehicle body attitude control device 1 hardly expands and contracts, and only the hydraulic damper 2R expands. Therefore, when the vehicle body B is inclined in order to reduce such excess centrifugal force, Since each hydraulic damper 2R, 2L generates almost no damping force, it does not hinder the tilting operation of the vehicle body B during traveling in the curved section. Even if there is a sinking of the gas spring A that supports the weight of the left side of the vehicle body B due to the inclination of the vehicle body B, the stroke speeds of the hydraulic dampers 2R and 2L will be different. Since the hydraulic damper 2L interposed on the left side of the vehicle body B exerts a damping force and suppresses the sinking of the vehicle body B, the hydraulic damper 2R interposed on the right side of the vehicle body B exhibits a small damping force. The lifting operation of the body B of the gas spring A is not hindered.

Further, when the railway vehicle V goes off the curved section and travels in the straight section, the vehicle body B is returned to the previous inclination, and the body B is moved horizontally with respect to the carriage T1 (T2). However, since the operation is to restore the height of the right side of the vehicle body B, only the hydraulic damper 2R contracts . At this time , a large difference occurs in the stroke speeds of the hydraulic dampers 2R, 2L, so that the generated damping force of the hydraulic damper 2R becomes extremely small, and hinders the operation of returning the inclination of the vehicle body B to the horizontal. Nor.

Then, after the operation of returning to the horizontal is completed, when the vehicle body B tries to tilt to the right side that is the opposite side beyond the horizontal state, the hydraulic dampers 2R and 2L are in reverse phase and substantially equal. Since each of the hydraulic dampers 2R, 2L exerts a large damping force because it expands and contracts at the stroke speed, it suppresses the inclination of the vehicle body B to the opposite side, shakes the vehicle body B back, It is possible to improve the problem of causing hunting in which B swings in the left-right direction (rolling).

  Further, when the vehicle body B in the railway vehicle V rolls due to a trajectory error or a centrifugal force due to turning, the vehicle body B rolls around the roll center, so that the hydraulic dampers 2R and 2L are in reverse phase. Will expand and contract at approximately the same stroke speed. Therefore, the hydraulic dampers 2R and 2L exert a large damping force against such rolling of the vehicle body B, and effectively suppress rolling of the vehicle body B.

  Further, when the vehicle body B in the railway vehicle V is vibrated in the vertical direction due to the vertical track deviation, the hydraulic dampers 2R and 2L are expanded and contracted at the same phase and substantially the same stroke speed. become. Therefore, the hydraulic dampers 2R and 2L also exert a large damping force against the vertical vibration of the vehicle body B, and suppress the vertical vibration of the vehicle body B.

  As can be understood from the above description, in the vehicle body attitude control device 1, the vehicle body B of the railway vehicle V that is traveling in a curved section is tilted to relieve excess centrifugal force, or from the curved section traveling to the straight section traveling. Since these operations are not hindered with respect to the operation of returning the vehicle body B to the horizontal state at the time of switching to the vehicle body, the vehicle body B is in an inclined state without impairing the responsiveness of the vehicle body inclination control when the railway vehicle V is traveling on a curve. When returning to the horizontal state, the vehicle body B is effectively prevented from tilting to the opposite side, the vehicle body B swinging back, and the vehicle body B hunting, and the vehicle body B rolling and vertical vibrations are suppressed. Can do.

  In other words, according to the attitude control device of the present invention, it is possible to generate a smaller damping force as the stroke speed difference of the hydraulic damper increases, which is effective for rolling, pitching and vertical vibration in the body of a railway vehicle. The vehicle can be comfortably controlled, and the ride comfort in the vehicle can be improved. Rolling due to the vehicle body returning too much can be prevented, which is optimal for vehicle body posture control of a railway vehicle.

  Therefore, in the vehicle body attitude control device 1, the riding comfort in the railway vehicle V can be dramatically improved.

  Next, the arrangement of the vehicle body attitude control device 1 with respect to the railway vehicle V will be described. As described above, the hydraulic dampers 2R and 2L are disposed between the carriage T1 (T2) of the railway vehicle V and the vehicle body B so as to be arranged on the left and right with respect to the vehicle traveling direction. In this way, a hydraulic damper 2R is interposed between the bogie T1 and the vehicle body B in front of the railway vehicle V, and a hydraulic damper 2L is interposed between the bogie T2 and the vehicle body B behind the rail vehicle V. Thus, the vehicle body attitude control device 1 can be arranged on each of the left and right sides.

  In this way, by disposing the hydraulic dampers 2R and 2L between the front and rear carriages T1 and T2 and the vehicle body B, the pitching of the vehicle body B can be suppressed, and the trajectory in the vertical direction is also changed. In some cases, when the railway vehicle V passes through such a place where the trajectory is out of order, the front carriage T1 first passes through the place where the trajectory is out of order, and then the rear carriage T2 passes through the place where the trajectory is out of order. become. The hydraulic damper 2R expands and contracts when the front truck T1 passes through the place where the trajectory is out of order, but the hydraulic damper 2R disposed on the rear truck T2 does not expand and contract, so the hydraulic damper 2R generates almost no damping force. Even if it occurs, the damping force is small. Further, when the rear truck T2 passes through the place where the trajectory is out of order, the hydraulic damper 2L expands and contracts, but the hydraulic damper 2R disposed in the front truck T1 does not expand and contract, so the hydraulic damper 2L has a damping force. Little or no damping force is generated.

  Therefore, for a vibration mode in which vibration is sequentially input before and after the vehicle body B, such as when the railway vehicle V passes through a track having such a vertical track error, the vehicle body attitude control device 1 The generated damping force of the hydraulic dampers 2R, 2L in the vehicle is reduced, and vibrations are hardly transmitted from the carriages T1, T2 to the vehicle body B. In addition to this, the hydraulic pressure is applied to the pitching in which the vehicle body B swings back and forth. The generated damping force of the dampers 2R and 2L can be increased to suppress pitching, and the riding comfort in the vehicle can be improved.

  In addition, the expansion and contraction of the hydraulic dampers 2R and 2L have the same phase with respect to rolling, and the vehicle body attitude control device 1 is disposed on each of the left and right with respect to the vehicle traveling direction, so that rolling of the vehicle body B is suppressed. It becomes possible.

Further, as shown in FIG. 7, in the railway vehicle V connected to the front and rear, a hydraulic damper 2 </ b> R is interposed between the rear truck T <b> 2 and the vehicle body B of the front railway vehicle V to It is also possible to dispose the damper 2L between the front carriage T1 of the rear rail vehicle V and the vehicle body B, and to arrange the vehicle body attitude control devices 1 on the left and right sides with respect to the vehicle traveling direction.

Since the vehicle bodies B in the front and rear rail vehicles V are connected by a coupler, for example, when the vehicle body B of a certain rail vehicle body V pitches, the vehicle body B of the rail vehicle V behind it pitches in the opposite direction. As described above, by arranging the vehicle body posture control device 1, the pitching of the vehicle body B can be suppressed.

In addition, when there is a vertical deviation in the track, the front and rear rail cars V pass through such a course deviation place, and the carriage T2 on the rear side of the front railway vehicle V first detects the course deviation place. After that, the carriage T1 on the front side of the rear rail vehicle V passes through the place where the trajectory is out of order. The hydraulic damper 2R expands and contracts when the rear truck T2 on the rear side of the rail vehicle V passes through the wrong track, but the hydraulic damper 2L disposed on the front truck T1 of the rear rail vehicle V does not expand and contract. Therefore, the hydraulic damper 2R generates little or no damping force even if it generates little damping force. Further, when the front truck T1 of the rear railway vehicle V passes through the track misalignment, the hydraulic damper 2L expands and contracts, but the hydraulic damper 2R disposed on the rear truck T2 of the front railway vehicle V Since it does not expand and contract, the hydraulic damper 2L generates little or no damping force even if it generates little damping force.

Therefore, the vehicle body attitude control is applied to a vibration mode in which vibrations are sequentially input to the preceding and following railcars V, such as when the railcars V pass through a trajectory having a vertical trajectory error. The generated damping force of the hydraulic dampers 2R and 2L in the apparatus 1 is reduced, and vibration is hardly transmitted from the carriages T1 and T2 to the vehicle body B. In addition to this, for pitching in which the vehicle body B swings back and forth. The generated damping force of the hydraulic dampers 2R and 2L can be increased to suppress pitching, and the riding comfort in the vehicle can be improved.

  In addition, the expansion and contraction of the hydraulic dampers 2R and 2L have the same phase with respect to rolling, and the vehicle body attitude control device 1 is disposed on each of the left and right with respect to the vehicle traveling direction, so that rolling of the vehicle body B is suppressed. It becomes possible.

  In addition, as shown in FIG. 8, a hydraulic damper 2R is provided between the carriage T1 and the vehicle body B and a hydraulic damper 2R is provided between the vehicle T2 and the vehicle body B in each of the left and right sides of the traveling direction of the plurality of railway vehicles V. The hydraulic damper 2L may be interposed, and the hydraulic damper 2R and the hydraulic damper 2L disposed in the adjacent railway vehicle V may be connected via the center block 20. In this case, the hydraulic dampers 2R and 2L interposed in order between the vehicle body B and the carriages T1 and T2 of the plurality of railway vehicles V are connected in a so-called daisy chain.

  Even in this case, the operation is the same as that shown in FIGS. 6 and 7. In this case, in addition to the vibration mode in which vibrations are sequentially input before and after the vehicle body B, the adjacent railways are operated. With respect to a vibration mode in which vibrations are sequentially input to the vehicle V, the generated damping force of the hydraulic dampers 2R and 2L in the vehicle body attitude control device 1 is reduced, and vibration is transmitted from the carriages T1 and T2 to the vehicle body B. It becomes difficult. In addition to this, the damping force generated by the hydraulic dampers 2R and 2L is increased with respect to the pitching in which the vehicle body B swings back and forth, thereby suppressing the pitching and further improving the ride comfort in the vehicle. can do.

Further, as shown in FIG. 9, a hydraulic damper 2R disposed on the right and left with respect to the vehicle traveling direction on the side of the truck T2 after the front of the rail vehicle V, and 2L, the rear of the rail vehicle V of the front bogie T1 The hydraulic dampers 2 </ b> R and 2 </ b> L arranged on the left and right with respect to the vehicle traveling direction can also be connected in a ring shape via the center block 20.

  Even in this case, the operation is the same as that shown in FIGS. 6 and 7. In this case, in addition to the vibration mode in which vibrations are sequentially input before and after the vehicle body B, the adjacent railways are operated. With respect to a vibration mode in which vibrations are sequentially input to the vehicle V, the generated damping force of the hydraulic dampers 2R and 2L in the vehicle body attitude control device 1 is reduced, and vibration is transmitted from the carriages T1 and T2 to the vehicle body B. It becomes difficult. In addition to this, the damping force generated by the hydraulic dampers 2R and 2L is increased with respect to the pitching in which the vehicle body B swings back and forth, thereby suppressing the pitching and further improving the ride comfort in the vehicle. can do.

In addition, when the formation vehicle travels in the curved section and performs the vehicle body tilt control, the vehicle body B of the railway vehicle V in the formation vehicle may be inclined in the order in which it enters the curved section. A state occurs in which the vehicle body B that is inclined but has not entered the curved section is not inclined. In such a case, according to the arrangement and connection of the hydraulic dampers 2R and 2L shown in FIG. 9, the hydraulic damper 2R (2L) arranged in one railcar V of the front and rear railcars V and the other The stroke speed is different from that of the hydraulic damper 2L (2R) disposed in the railway vehicle V, and the hydraulic dampers 2R and 2L disposed in the same railway vehicle V are also left and right. As a result, the generated damping force of each of the hydraulic dampers 2R, 2R, 2L, 2L becomes small, and the vehicle body tilt control as described above is not hindered.

Furthermore, in the arrangement shown in FIG. 10, hydraulic dampers 2R and 2L arranged on the left and right with respect to the vehicle traveling direction between the vehicle body B of the railway vehicle V and the front carriage T1, and the vehicle body B of the railway vehicle V The hydraulic dampers 2R and 2L arranged on the left and right with respect to the traveling direction of the vehicle between the rear carriage T2 are connected annularly through the center block 20 and arranged in the same manner as the front and rear railway vehicles V. The hydraulic dampers 2R and 2L to be connected are connected annularly via the center block 20.

Even in this case, the operation is the same as that shown in FIGS. 6 and 7, and in this case, in addition to the vibration mode in which vibration is input in order before and after the vehicle body B, the operation is performed before and after. With respect to a vibration mode in which vibration is sequentially input to the railway vehicle V, the generated damping force of the hydraulic dampers 2R and 2L in the vehicle body attitude control device 1 is reduced, and vibration is transmitted from the carriages T1 and T2 to the vehicle body B. It becomes difficult to be done. In addition to this, the damping force generated by the hydraulic dampers 2R and 2L is increased with respect to the pitching in which the vehicle body B swings back and forth, thereby suppressing the pitching and further improving the ride comfort in the vehicle. can do.

In addition, when the formation vehicle travels in the curved section and performs the vehicle body tilt control, the vehicle body B of the railway vehicle V in the formation vehicle may be inclined in the order in which it enters the curved section. A state occurs in which the vehicle body B that is inclined but has not entered the curved section is not inclined. In such a case, according to the arrangement and connection of the hydraulic dampers 2R and 2L shown in FIG. 10, it is arranged on one rail vehicle V of the front and rear rail vehicles V, similar to that shown in FIG. There is a difference in stroke speed between the hydraulic damper 2R (2L) and the hydraulic damper 2L (2R) arranged in the other railway vehicle V, and the liquid damper 2R (2L) arranged in the same railway vehicle V Since the pressure dampers 2R and 2L also have a difference in the left and right stroke speed, the damping force generated by each hydraulic damper 2R, 2R, 2L, and 2L is reduced, and the vehicle body tilt control as described above is not hindered. .

Further, according to the arrangement and connection of FIG. 10, when propagation of vertical and rolling vibrations sequentially occurs in the front and rear rail vehicles V, such as when passing through a tunnel or passing each other between trains, A difference in stroke speed is generated between the hydraulic dampers 2R and 2L mounted on the front and rear railway vehicles V, and the damping force of the hydraulic dampers 2R and 2L is reduced, so that vibration transmission between the railway vehicles V is prevented. Is possible.

  Furthermore, in the arrangement shown in FIG. 11, the hydraulic damper 2R in one vehicle body attitude control device 1 is interposed on one side with respect to the vehicle traveling direction between the rear vehicle T2 and the vehicle body B of the railway vehicle V. The hydraulic damper 2L is interposed on the other side with respect to the vehicle traveling direction between the carriage T1 on the front side of the railway vehicle V and the vehicle body B behind the railway vehicle V, and the second vehicle body attitude control is performed. The hydraulic damper 2R in the apparatus 1 is interposed on the other side with respect to the vehicle traveling direction between the carriage T2 on the rear side of the railway vehicle V and the vehicle body B, and the hydraulic damper 2L is installed on the railway behind the railway vehicle V. The vehicle body V is interposed on one side with respect to the vehicle traveling direction between the vehicle T1 on the front side of the vehicle V and the vehicle body B, and the two vehicle body attitude control devices 1 are arranged in a so-called stake.

In this case, it is possible to suppress rolling and pitching of the vehicle body B, and it is also possible to suppress relative rolling between the vehicle bodies B in the front and rear rail vehicles V. In addition, as a technique for suppressing such relative rolling between the vehicle bodies B, there is known a technique in which a damper called a vehicle end damper is interposed between the vehicle bodies B, and in such a vehicle end damper, , It must be provided in a position that avoids the passage provided between the vehicle bodies B, and it becomes very long and a large bending moment is applied. This causes rattling and noise, causing passengers to feel uncomfortable. However, the vehicle body attitude control device 1 can suppress the relative rolling between the vehicle bodies B as in the case of the vehicle end damper, and does not need to be installed between the vehicle bodies B as described above. , no fear of the expense of the passage area between the vehicle body B, also hydraulic damper 2R, 2L large can stay short because it is interposed between the vehicle body B and the bogie T1 (T2) Bending mode Since nor cement acts, since backlash is less likely to occur, it can be suppressed generation of noise, nor discomfort to passengers.

  Furthermore, in the arrangement shown in FIG. 12, the hydraulic damper 2R in one vehicle body attitude control device 1 is interposed on one side with respect to the vehicle traveling direction between the front carriage T1 and the vehicle body B, and the hydraulic damper 2L is interposed on the other side with respect to the vehicle traveling direction between the rear carriage T1 and the vehicle body B, and the hydraulic damper 2R in the second vehicle body attitude control device 1 is connected to the front carriage T1 and the vehicle body B. The hydraulic damper 2L is interposed on one side with respect to the vehicle traveling direction between the rear carriage T2 and the vehicle body B, and The two vehicle body attitude control devices 1 are arranged in the same railway vehicle V so-called as if they are marked.

  In this case, the hydraulic dampers 2R and 2L in the vehicle body attitude control device 1 are in response to a vibration mode in which vibrations are input in order before and after the vehicle body B in the same manner as shown in FIGS. The generated damping force is reduced, and vibration is hardly transmitted from the carriages T1 and T2 to the vehicle body B. Furthermore, the damping force generated by the hydraulic dampers 2R and 2L is increased with respect to the pitching in which the vehicle body B swings back and forth and the rolling in which the vehicle body swings left and right, so that the pitching and rolling can be suppressed. For the tilt control, the generated damping force of the hydraulic dampers 2R and 2L is small, so that the operation of returning the tilt and tilt of the vehicle body B is not hindered.

  In the arrangement and connection of the hydraulic dampers 2R and 2L shown in FIGS. 6 to 12, the hydraulic dampers 2R and 2L have a large damping force when the entire vehicle body B vibrates uniformly in the vertical direction. Of course, in addition to pitching and rolling of the vehicle body B, it is possible to suppress vertical vibration.

Finally, a vehicle body attitude control device 50 according to another embodiment will be described. In the vehicle body attitude control device 50 according to the other embodiment, as shown in FIG. 13, the hydraulic dampers 51R and 51L are set in a double rod type, and the two pressures of the hydraulic dampers 51R and 51L are set. chamber X, Y each damping valve 52R, the damping passage 53R with the 52L, connected by 53L, connected Kakueki圧damper 51R, two pressure chambers X of 51L, Y each bypass passage 54R, in 54L, bypass On-off valves 55R and 55L are provided in the middle of the passages 54R and 54L, respectively. The on-off valve 55R uses the pressure in one pressure chamber X (Y) of each of the hydraulic dampers 51R and 51L as a pilot pressure, and the pressure in one pressure chamber X (Y) of the hydraulic damper 51R. When the pressure exceeds the pressure in one pressure chamber X (Y) of the hydraulic damper 51L by a predetermined amount, the bypass passage 54R is opened, and the other on-off valve 5L has one of the hydraulic dampers 51R and 51L. Using the pressure in X (Y) as a pilot pressure, the pressure in one pressure chamber X (Y) of the hydraulic damper 51L exceeds the pressure in one pressure chamber X (Y) of the hydraulic damper 51R by a predetermined amount. The bypass passage 54L is opened.

  Therefore, even in the vehicle body posture control apparatus 50 according to the other embodiment, it is possible to operate in the same manner as the vehicle body posture control apparatus 1 according to the one embodiment, and the same effects can be obtained.

  This is the end of the description of the embodiment of the present invention, but the scope of the present invention is of course not limited to the details shown or described.

It is a top view of a railway vehicle. It is a side view of a railway vehicle. It is the figure shown notionally of the vehicle body attitude | position control apparatus in one Embodiment. It is the figure which showed the specific structure of the integrated on-off valve. It is the figure which showed other specific structures of the integrated on-off valve. It is the figure which showed an example of arrangement | positioning with respect to the railway vehicle of the hydraulic damper in a vehicle body attitude | position control apparatus. It is the figure which showed an example of arrangement | positioning with respect to the railway vehicle of the hydraulic damper in a vehicle body attitude | position control apparatus. It is a figure which shows an example of arrangement | positioning with respect to the railway vehicle of the hydraulic damper in a vehicle body attitude | position control apparatus. It is the figure which showed an example of arrangement | positioning with respect to the railway vehicle of the hydraulic damper in a vehicle body attitude | position control apparatus. It is the figure which showed an example of arrangement | positioning with respect to the railway vehicle of the hydraulic damper in a vehicle body attitude | position control apparatus. It is the figure which showed an example of arrangement | positioning with respect to the railway vehicle of the hydraulic damper in a vehicle body attitude | position control apparatus. It is the figure which showed an example of arrangement | positioning with respect to the railway vehicle of the hydraulic damper in a vehicle body attitude | position control apparatus. It is the figure which showed notionally the vehicle body attitude | position control apparatus in other embodiment.

1,50 Car body attitude control device 2R, 2L, 51R, 51L Hydraulic damper 3R, 3L, 52R, 52L Damping valve 4R, 4L, 54R, 54L Bypass passage 5R, 5L, 55R, 55L Open / close valve 10 Cylinder 11 Piston 12 Rod 13 Tank 14, 43, 44, 53R, 53L Damping passage 15, 17 Check valve 16 Suction passage 18 Outer cylinder 20 Center block 21 Valve body 22, 34, 35 Spring 31, 32 Chamber 33, 40 Spool 20a, 20b Port 20c Tank port 41 Small-diameter portion 42 Annular seal A Gas spring B Car body P Piston side chamber R Rod side chamber T1 Front cart T2 Rear cart V Railway vehicle X, Y Pressure chamber

Claims (11)

It has a damping valve that resists the flow of liquid during expansion and contraction, a bypass passage that bypasses the damping valve, and an on-off valve provided in the middle of each bypass passage. Two or more hydraulic dampers, and an on-off valve in any one of the hydraulic dampers bypasses the bypass passage when the pressure in the hydraulic damper exceeds the pressure in any other hydraulic damper by a predetermined amount. A vehicle body posture control device characterized by opening. The hydraulic damper is set to a single rod uniflow type, connecting the rod side chamber of each hydraulic damper and the tank with a damping passage provided with a damping valve, respectively, and connecting the rod side chamber and tank of each hydraulic damper to the bypass passage, respectively. And a suction passage that connects the piston-side chamber of each hydraulic damper and the tank is provided, and the open / close valve in any one hydraulic damper has a pressure in the rod-side chamber of the hydraulic damper that is not limited to any other liquid. The vehicle body attitude control device according to claim 1, wherein the bypass passage is opened when the pressure in the rod side chamber of the pressure damper exceeds a predetermined amount. The vehicle body posture control device according to claim 2, wherein the hydraulic damper includes a tank on an outer periphery. The hydraulic damper is set as a double rod type, and the two pressure chambers of each hydraulic damper are connected by a damping passage with a damping valve, and the two pressure chambers of each hydraulic damper are connected by a bypass passage. The on-off valve in any one hydraulic damper opens the bypass passage when the pressure in the pressure chamber on one side of the hydraulic damper exceeds the pressure in the pressure chamber on one side of any other hydraulic damper by a predetermined amount. The vehicle body posture control device according to claim 1. The on-off valve has a hollow housing, a spool defining two chambers in the housing, a port connecting one chamber to a bypass passage in any one hydraulic damper, and any other chamber connecting any other chamber. A port that connects to the bypass passage in the hydraulic damper and a tank port that connects the inside of the housing to the tank via the bypass passage. When there is no difference in the pressure in each room, the outer periphery of the spool is connected to the tank port. When the pressure in one chamber communicating with any one hydraulic damper exceeds the pressure in the other chamber communicating with any other hydraulic damper by a predetermined amount, the spool is moved to the other chamber side. The tank port is moved to communicate with the tank port, and the tank port is connected to the tank in any one hydraulic damper via the bypass passage in any one hydraulic damper. Vehicle attitude control device according to claim 2 or 3, characterized in that communicating with the click. 6. The vehicle body attitude control device according to claim 1, wherein the on-off valve in any one hydraulic damper and the on-off valve in any other hydraulic damper are housed in one housing. 6. The vehicle body attitude control device according to claim 5, wherein a damping passage is provided in the spool. The vehicle body attitude control device according to claim 2, 3, 5, or 6, wherein the rod cross-sectional area of the hydraulic damper is set to one half of the piston cross-sectional area. The vehicle body attitude control device according to any one of claims 1 to 8, wherein hydraulic dampers are arranged on the left and right sides with respect to the vehicle traveling direction between the carriage and the vehicle body. The vehicle body attitude control device according to any one of claims 1 to 9, wherein a hydraulic damper is disposed between each of the front and rear carriages and the vehicle body of the railway vehicle. The vehicle body attitude control device according to any one of claims 1 to 10, wherein a hydraulic damper is disposed between each of a carriage and a vehicle body in adjacent railway vehicles.

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