JP2014016011A - Control valve using pendulum angle - Google Patents

Abstract

PROBLEM TO BE SOLVED: To properly output a control air pressure utilizing a pendulum angle by a control valve using a pendulum.SOLUTION: A control valve 10 using a pendulum angle includes a pendulum 12, a spool 56 which is driven by the pendulum 12 and provided with a first land and a second land, a sleeve 54 which supports the spool 56 movably in an axial direction, and has a support port, a first load port, a second load port, and an exhaust port, and a spring part which applies elastic force for axial displacement of the spool 56 and a damper part which applies damping force. The first load port and second load port both communicate with the exhaust port when the spool 56 is at a neutral position for the sleeve 54, the first load port communicates with the support port when the spool is displaced from the neutral position exceeding a first dead-zone displacement quantity, and the second load port communicates with the support port when the spool is displaced in the opposite direction exceeding a second dead zone displacement quantity.

Description

  The present invention relates to a control valve that uses a pendulum angle, and more particularly to a control valve that uses a pendulum angle that is used to generate a vehicle body tilt control gas pressure.

  Normally, a canal is provided on a curved track of a railway vehicle, but if the vehicle runs on a curve at a speed higher than the equilibrium speed determined from the cant amount, an excessive centrifugal acceleration that cannot be canceled by the cant is generated and the ride comfort becomes worse. . Therefore, vehicle body tilt control is performed so that the vehicle body can be further tilted so that the resultant force of the excess centrifugal acceleration and gravity works perpendicularly to the vehicle body floor surface. A pendulum type vehicle is known as one that enables such vehicle body inclination.

  For example, in Patent Document 1, as a body tilting device for a pendulum type vehicle, a roller device is provided in a carriage shape, and a curved pendulum beam is coupled to the roller device via a spring device such as an air spring. Further, it is described that a cylinder provided between a pendulum beam and a carriage is actuated by a signal from an operation controller to tilt the vehicle body.

  Here, as a control signal to the operation controller, it is assumed that the speed is detected by the speed detector, and the optimum inclination angle is calculated by the arithmetic unit from the curve shape information of the traveling route collected and stored in advance. ing.

  Patent Document 2 discloses an automatic height adjustment mechanism (LV) that automatically adjusts the vehicle height, which is the height of the vehicle body relative to the carriage, in response to an increase or decrease in the number of passengers as a vehicle body posture control device for a railway vehicle. A structure is disclosed in which the LV is rotatably supported and a weight is provided on the LV. Here, when the railway vehicle travels at a high speed on a curve and an excessive centrifugal acceleration acts, the weight causes the LV to rotate with respect to the vehicle body, thereby supplying air to the air spring on the outer gauge side and It is stated to increase the vehicle height.

JP 2002-67944 A JP 2010-137622 A

  For travel routes with many straight sections, it is sufficient to incline the vehicle body because the excess centrifugal acceleration has reached a certain level, without having to calculate the optimum inclination angle by a computing unit. In such a case, it is conceivable that the structure can be simplified by using a pendulum that swings according to the excess centrifugal acceleration and generating a control gas pressure for tilting the vehicle body based on the pendulum angle.

  However, since the vibration component is superimposed on the pendulum movement due to the vibration of the vehicle, it cannot be used to generate a control gas pressure that tilts the vehicle body while maintaining the pendulum angle. In addition, in order to generate a control gas pressure for tilting the vehicle body when the pendulum angle is equal to or larger than a predetermined set pendulum angle, it is necessary to provide a predetermined dead zone with respect to the pendulum angle. Thus, a problem remains in order to generate a control gas pressure for tilting the vehicle body using the pendulum angle. Note that Patent Document 2 corresponds to using the automatic height adjusting device itself as a pendulum, but since the rotational resistance of the shaft inside the automatic height adjusting device is large, a considerably large weight is required for rotation with excess centrifugal acceleration. Is required.

  An object of the present invention is to provide a control valve using a pendulum angle that can appropriately output a vehicle body tilt control gas pressure.

  The control valve using the pendulum angle according to the present invention is driven according to the pendulum motion around the predetermined rotation center in response to the acceleration, and driven according to the pendulum angle of the pendulum, and is controlled along the axial direction of the stem. A spool provided with one land and a second land, a supply port for supporting the spool in an axially movable manner and supplying a gas having a supply gas pressure, and a first land provided corresponding to the first land and the second land A sleeve having a load port, a second load port, an exhaust port for exhausting to the outside, a spring portion for providing an elastic force having a predetermined spring constant with respect to the axial displacement of the spool, and for the axial displacement of the spool, It is preferable to include a damper portion that provides a damping force having a predetermined damping constant, and a pendulum damper that suppresses free vibration of the pendulum.

  In the control valve using the pendulum angle according to the present invention, when the spool is in the neutral position with respect to the sleeve, both the first load port and the second load port are in a positional relationship communicating with the exhaust port. Accordingly, when the spool is displaced from the neutral position toward the second load port side of the sleeve, the first load port is once blocked by the first land, and further exceeds a predetermined first dead band displacement amount. The first load port communicates with the supply port by the displacement of the first load port. When the spool is displaced from the neutral position toward the first load port side of the sleeve according to the pendulum angle, the second load port is After being shut off by the two lands, the second load port is supplied to the supply port by performing a predetermined displacement exceeding the predetermined second dead zone displacement. It is preferable that a positional relationship of preparative communicating with.

  Further, in the control valve using the pendulum angle according to the present invention, the rotation center of the pendulum provided in the casing including the sleeve, and the spool side provided integrally with the pendulum on the opposite side of the pendulum across the rotation center of the pendulum And a spring seat provided at the spool-side tip. The spring portion is a first coil spring provided between the first land-side end of the spool and the spring seat, and the second land side of the spool. The damper includes a second coil spring provided between the end portion of the spool and the spring seat, and the damper portion includes a first gas between the end portion on the first land side of the spool and the inner wall of the end portion on the first load port side of the sleeve. The space and the second gas space between the end portion on the second land side of the spool and the inner wall of the end portion on the second load port side of the sleeve are used in communication with each other via the throttle portion. Is preferred.

  With the above configuration, the control valve that uses the pendulum angle uses a spool / sleeve mechanism having a spool that is driven according to the pendulum angle, and provides a spring portion that provides an elastic force having a predetermined spring constant with respect to the axial displacement of the spool. And a damper portion that provides a damping force having a predetermined damping constant with respect to the axial displacement of the spool. By appropriately setting the spring constant and the damping constant, even when vibration is applied to the rotation center, the influence of the vibration on the pendulum motion can be suppressed, and the pendulum angle can be used for control.

  In addition, since the pendulum damper that suppresses the free vibration of the pendulum is provided, the tilt control of the vehicle can be appropriately performed using the pendulum angle that is not affected by the free vibration of the pendulum.

  As for the land position of the spool and the load port position of the sleeve, in the neutral position, both load ports communicate with the exhaust port, and when the spool is displaced beyond the first dead zone displacement, the supply gas pressure is applied to the first load port. The output gas pressure is set so that the supply gas pressure is output to the second load port when the spool is displaced beyond the second dead zone displacement amount. By setting in this way, the vehicle tilt control gas pressure can be generated for the first time when the pendulum angle becomes a certain size and exceeds the first dead zone displacement amount or the second dead zone displacement amount.

  Further, in the control valve using the pendulum angle, a spring seat is provided at the front end of the spool side that is provided integrally with the pendulum on the opposite side of the pendulum across the rotation center of the pendulum. A spring portion is provided between the spring seat and the spool, and a space formed between the spool end and the sleeve end is used as a damper portion, so that a pendulum angle having an appropriate damping characteristic can be obtained while being small. The control valve used can be used. In addition, since the throttle portion is provided in the communication path connecting the first gas space and the second gas space, the degree of freedom in setting the damping constant of the damper portion is increased.

It is a block diagram of the control valve using the pendulum angle of the embodiment according to the present invention. It is sectional drawing of the neutral state of the control valve using the pendulum angle of embodiment which concerns on this invention. It is sectional drawing which shows when a pendulum rotates in the control valve using the pendulum angle of embodiment which concerns on this invention. It is a figure which shows the relationship between a pendulum angle etc. and the output of a load port in the control valve using the pendulum angle of embodiment which concerns on this invention. It is a figure which shows the vibration model of the control valve using the pendulum angle of embodiment which concerns on this invention.

  Embodiments according to the present invention will be described below in detail with reference to the drawings. In the following description, it is assumed that the space between the spool and the sleeve is used as the damper portion in the spool / sleeve mechanism, but an external damper portion may be provided.

  The frequency, angle, and the like described below are examples for explanation, and can be appropriately changed according to the specification of the control valve using the pendulum angle.

  Below, the same code | symbol is attached | subjected to the same element in all the drawings, and the overlapping description is abbreviate | omitted. In the description in the text, the symbols described before are used as necessary.

  FIG. 1 is a configuration diagram of a control valve 10 using a pendulum angle. The control valve 10 using the pendulum angle includes a pendulum 12, a pendulum damper 30 provided in the housing unit 14, and a spool / sleeve mechanism 50. The control valve 10 using the pendulum angle performs the axial drive of the spool 56 of the spool-sleeve mechanism 50 by using the pendulum movement of the pendulum 12 that can rotate about the rotation center 16 provided in the housing unit 14. The outputs of the first load port 104 and the second load port 108 which are the two load ports of the sleeve 54 are controlled.

  The control valve 10 using the pendulum angle can be provided, for example, on the body of a railway vehicle. In that case, the magnitude of the excess centrifugal acceleration that occurs when the railway vehicle travels in the curved section is detected by the pendulum angle that is the rotation angle of the pendulum 12, and in response to this detection, the first load port 104 and the second load port The output of 108 is controlled.

  The pendulum 12 is a weight that is a mass body that rotates around the rotation center 16. In FIG. 1, the pendulum 12 is shown as a spherical shape, but may have a shape other than the spherical shape. For example, a disk shape may be sufficient and a rectangular plate shape, an ellipse plate shape, etc. may be sufficient. When the pendulum 12 receives an acceleration acting on its mass, the pendulum 12 rotates around the rotation center 16. In FIG. 1, the acceleration received by the pendulum 12 is denoted by α, and the pendulum angle that is the rotation angle around the rotation center 16 of the pendulum 12 is denoted by θ.

  The housing | casing part 14 is a case which comprises the main body of the control valve 10 using a pendulum angle. The housing portion 14 is provided with a rotation center 16, a pendulum damper 30, and a spool / sleeve mechanism 50.

  The rotation center 16 is a rotation support shaft provided in the housing portion 14 and has a function of supporting the pendulum 12 rotatably around the shaft. The rotation center 16 may be a rotation support hole provided in the housing portion 14, and the pendulum 12 may be rotatably supported around the rotation support hole.

  The connecting shaft 20 connects the pendulum 12, the rotation center 16, the pendulum damper 30, and the spool / sleeve mechanism 50, and has a function of transmitting the movement of the pendulum 12 around the rotation center 16 to the pendulum damper 30 and the spool / sleeve mechanism 50. It is a member. The connecting shaft 20 includes a center disk 24 provided corresponding to the rotation center 16, a sphere 32 provided corresponding to the pendulum damper 30, and a sphere 52 provided corresponding to the spool / sleeve mechanism 50. This is an elongated shaft body in which these are connected by a pendulum side arm 22 and a spool side arm 26.

  The center disk 24 is a rotating disk provided with a hole corresponding to the rotation support shaft of the rotation center 16. As described above, when the rotation center 16 is a rotation support hole, a rotation shaft corresponding to the rotation support hole is provided. The pendulum side arm 22 connects between the center disk 24 and the pendulum 12.

  The spool side arm 26 is provided in a form in which the pendulum side arm 22 is extended on the opposite side of the pendulum 12 with the rotation center 16 in between. The spherical body 32 provided in the middle of the spool side arm 26 is a member that transmits the movement around the rotation center 16 of the pendulum 12 to the moving body 36 of the pendulum damper 30. The sphere 52 provided at the tip of the spool side arm 26 is a member having a function of transmitting the motion of the pendulum 12 around the rotation center 16 to the spool 56 of the spool / sleeve mechanism 50.

  The pendulum damper 30 includes a damper housing 34 having an internal space and a moving body 36 disposed in the internal space of the damper housing 34. The internal space of the damper housing 34 is a cylindrical cavity, and the moving body 36 is a cylindrical body that slides in the cylindrical cavity. The damper spaces 38 and 40 shown in FIG. 1 are spaces formed between inner walls at both axial ends of the internal space of the damper housing 34 and both ends of the moving body 36. The communication path 42 connects the damper spaces 38 and 40, and the throttle portion 44 is provided in the communication path 42 and has a function of restricting the gas flow between the damper spaces 38 and 40.

  The pendulum damper 30 includes a cylindrical portion 33 that can slide with respect to the sphere 32 of the connecting shaft 20. The spherical body 32 and the cylindrical portion 33 have a function of converting a rotational motion around the rotational center 16 of the pendulum 12 into a linear motion of the moving body 36. As shown in FIG. 1, when the pendulum 12 rotates about the rotation center 16 in the θ direction, the spool side arm 26 and the sphere 32 of the connecting shaft 20 rotate about the rotation center 16 in the θ direction. When the spherical body 32 makes an arc motion of θ around the rotation center 16, the spherical body 32 moves the cylindrical portion 33 in the X direction shown in FIG. The X direction is the axial direction of the pendulum damper 30. Note that the sliding direction of the sphere 32 with respect to the cylindrical portion 33 is a direction perpendicular to the X direction. In this way, the rotational movement in the θ direction around the rotation center 16 of the pendulum 12 is converted into the linear movement in the X direction of the moving body 36 in the pendulum damper 30.

  When the movable body 36 moves in the X direction in the pendulum damper 30, the volume of the damper spaces 38 and 40 changes. In the above case, since the moving body 36 moves in the X direction, the volume of the damper space 38 decreases and the volume of the damper space 40 increases. Since the damper spaces 38 and 40 communicate with each other through the communication passage 42 via the throttle portion 44, the movement of the moving body 36 in the X direction receives a damping force, and the pendulum damper 30 moves the pendulum 12. Acts as a damper.

  The role of the pendulum damper 30 as a damper is to suppress free vibration of the pendulum 12. That is, when the acceleration α applied to the pendulum 12 is to be detected at the pendulum angle θ, it is not necessary for the pendulum 14 to vibrate freely. This is because when the pendulum 14 freely vibrates, the pendulum angle θ is overlapped by acceleration α and free vibration. Therefore, the aperture amount of the aperture 44 is set so that the free vibration of the pendulum 14 is suppressed and the pendulum angle θ accurately reflects the acceleration α.

As free oscillation of the pendulum 14 is appropriately suppressed by the pendulum damper 30, the control valve 10 using the pendulum angle, the noise vibration N _A is applied for the housing 14. The noise vibration N _A is not due to the free vibration of the pendulum 12, but is due to the vibration of the object to which the housing portion 14 is attached. The noise vibration N _A is partially suppressed by the pendulum damper 30, but is mainly performed by a spring portion and a damper portion provided in the spool / sleeve mechanism 50. This will be described later.

  In FIG. 1, a sphere 52 provided between the tips of the spool side arm 26 transmits the movement of the pendulum 12 around the rotation center 16 to the spool 56 of the spool / sleeve mechanism 50. As shown in FIG. 1, when the pendulum 12 rotates θ around the rotation center 16, the sphere 52 also rotates θ around the rotation center 16.

  The spool / sleeve mechanism 50 incorporated in the housing unit 14 includes a spool 56 and a sleeve 54. The sleeve 54 is fixed to the housing unit 14. The detailed configuration and operation of the spool / sleeve mechanism 50 will be described with reference to FIGS.

  FIG. 2 is a view showing a neutral state of the spool / sleeve mechanism 50. The neutral state is a state where the pendulum 12 is hanging from the rotation center 16 in a natural state, and the center lines of the pendulum side arm 22 and the spool side arm 26 are parallel to the direction of gravity. In this neutral state, the sphere 52 is at the center position in the longitudinal direction of the spool / sleeve mechanism 50 and at the center position in the lateral direction. This state is a state where the spool 56 is in the neutral position with respect to the sleeve 54. The longitudinal direction of the spool / sleeve mechanism 50 is the X direction. Therefore, in the neutral state, θ = 0 and the position of the sphere 52 is X = 0.

  The spool 56 is a cylindrical member having a hollow space inside and having a longitudinal direction as an axial direction. The sleeve 54 is also a cylindrical member having a hollow space inside and having a longitudinal direction as an axial direction. The inner wall of the hollow space of the sleeve 54 has a function of slidably supporting the axial movement of the spool 56.

  The axial length of the hollow space of the sleeve 54 is set longer than the axial length of the outer diameter of the spool 56. That is, when the spool 56 is disposed in the hollow space of the sleeve 54 and is in a neutral state, the axial space between both ends of the hollow space of the sleeve 54 and both axial ends of the outer diameter of the spool 56 are respectively provided. A gas space is formed. The gas spaces at both ends act as damper spaces when the spool 56 moves in the axial direction. By distinguishing the two gas spaces, the gas space on the right side of the paper surface can be referred to as the first gas space 80, and the gas space on the left side of the paper surface in the X direction can be referred to as the second gas space 82.

  The communication path 84 connects the first gas space 80 and the second gas space 82, and the throttle portion 86 is provided in the communication path 84, and restricts the gas flow between the first gas space 80 and the second gas space 82. It has the function to do. What connected the 1st gas space 80 and the 2nd gas space 82 by the communicating path 84 via the throttle part 86 functions as a damper part.

  The spool 56 has a stem having a small radial dimension and a land having a large radial direction along the axial direction, where the longitudinal direction is the axial direction and the short side direction is the radial direction. There are a total of four lands, end lands 58 and 64 provided at both ends in the axial direction, and a first land 60 and a second land 62 provided between the end lands 58 and 64 along the axial direction of the stem. It is. When the end land on the first land 60 side is referred to as the first end land 58 and the end land on the second land 62 side is referred to as the second end land 64, in FIG. 2, along the axial direction of the spool 56, The first end land 58, the first land 60, the second land 62, and the second end land 64 are arranged in this order from the right side of the page toward the X direction on the left side of the page.

  A hollow space is provided in the spool 56. This internal cavity space is a cylindrical space along the axial direction. The spring seats 70 and 72 provided in the cylindrical space are members that can rotatably support the sphere 52 provided at the tip of the spool-side arm 26. As will be described later with reference to FIG. 3, when the spool side arm 26 rotates around the rotation center 16, the spring seats 70 and 72 cause the spherical body 52 at the tip of the spool side arm 26 to move on its cylindrical surface according to the rotation. To support.

  With such a structure, when the pendulum 12 rotates in the θ direction with respect to the rotation center 16 and the sphere 52 rotates in the θ direction, the spring seats 70 and 72 move in the X direction shown in FIG. The X direction is a direction from the first land 60 toward the second land 62. Conversely, when the pendulum 12 rotates in the direction opposite to the θ direction with respect to the rotation center 16, the spring seats 70 and 72 move in the direction from the second land 62 toward the first land 60.

  Spring portions are provided between the inner walls at both ends of the cylindrical space inside the spool 56 and the spring seats 70 and 72, respectively. In order to distinguish between the two spring portions, the spring portion on the right side of the paper surface can be referred to as the first coil spring 76, and the spring portion on the left side of the paper surface in the X direction can be referred to as the second coil spring 78. As for the spool 56, when the right end of the paper surface is the first end, and the left end of the paper is the second end portion in the X direction, the first coil spring 76 has one end at the first end of the spool 56. The other end is connected to the spring seat 70. The second coil spring 78 has the other end connected to the second end of the spool 56 and one end connected to the spring seat 72.

  When the spool / sleeve mechanism 50 is in a neutral state, the first coil spring 76 and the second coil spring 78 have the same axial length and are in a predetermined compressed state.

  The sleeve 54 has an inner wall that slidably supports the axial movement of the spool 56. Five openings are provided in the inner wall of the sleeve 54 along the axial direction. The five openings are arranged in the order of the first supply port 90, the first load port 92, the exhaust port 94, the second load port 96, and the second supply port 98 from the right side of the page toward the X direction on the left side of the page. Is done. The first supply port 90 and the second supply port 98 are connected to each other by the communication path 100.

The first load port 92 opens to the outside of the sleeve 54 as the first load port 104. The second load port 96 opens to the outside of the sleeve 54 as the second load port 108. The first load port 104 and the second load port 108 are used as ports for supplying a gas having a control gas pressure to the two loads. In FIG. 2, Q ₁ is shown in the first load port 104 and Q ₂ is shown in the second load port 108, and Q ₁ and Q ₂ represent gas flow rates flowing therethrough.

The first supply port 90 and the second supply port 98 connected to each other by the communication path 100 open to the outside of the sleeve 54. In FIG. 2, the first supply port 102 corresponding to the first supply port 90 and the second supply port 110 corresponding to the second supply port 98 are shown, but either one is opened to the outside of the sleeve 54. It's enough. Hereinafter, the description will be continued assuming that the first supply port 102 opens to the outside of the sleeve 54. The first supply port 102 is connected to a gas supply source (not shown), the gas is supplied with a supply gas pressure P _S a predetermined. In FIG. 2, the first supply port 102 and the second supply port 110 are shown as P _S , and this is shown. The exhaust port 94 opens to the outside of the sleeve 54 as an exhaust port 106. The exhaust port 106 is open to the atmosphere. 2 the exhaust port 106 shown as E _X, expressed it.

  The arrangement relationship between the first land 60 and the second land 62 of the spool 56 and the five openings of the sleeve 54 is set as follows. That is, when the spool 56 is in the neutral position with respect to the sleeve 54, the first load port 92 is in a position communicating with the exhaust port 94, and the second load port 96 is also in a position communicating with the exhaust port 94. Is set as follows.

  That is, in the state of being in the neutral position, the first land 60 does not completely close the first load port 92 and the first load port 92 and the first supply port 90 are blocked, but the first load port 92 92 and the exhaust port 94 communicate with each other. In addition, the second land 62 does not completely close the second load port 96 and the second load port 96 and the second supply port 98 are blocked, but the second load port 96 and the exhaust port 94 communicate with each other. To do.

  In FIG. 2, the gas flow at that time is changed from the first load port 104 to the first load port 92, from the first load port 92 to the stem between the first land 60 and the second land 62, and from the stem to the exhaust port. This is indicated by an arrow passing through the exhaust port 106 via 94. Similarly, the direction from the second load port 108 to the second load port 96, from the second load port 96 to the stem between the second land 62 and the first land 60, and from the stem to the exhaust port 106 via the exhaust port 94. The arrows indicate that gas flows.

  FIG. 3 is a diagram illustrating a state when the pendulum 12 rotates in the θ direction with respect to the rotation center 16 and the sphere 52 rotates in the θ direction with respect to the rotation center 16. At this time, the spring seats 70 and 72 are driven to move in the X direction by the rotational movement of the sphere 52 in the θ direction. When the spring seats 70 and 72 are driven to move in the X direction, the second coil spring 78 is further compressed, and the compressive force of the first coil spring 76 is weakened. Thus, the spool 56 serves to reduce the volume of the second gas space 82 while increasing the volume of the first gas space 80.

  Therefore, when the spring seats 70 and 72 move in the X direction, the elastic force of the first coil spring 76 and the second coil spring 78 that are two spring portions, and the first gas space 80 and the second gas space 82 are included. The spool 56 moves in the X direction while receiving the damping force of the damper portion.

When the spool 56 moves in the X direction from the neutral position, the positional relationship between the first land 60 and the second land 62 of the spool 56 and the five openings of the sleeve 54 is as shown in FIG. It is set as follows. Here, the vertical axis in FIG. 4 is the flow rate Q ₁ flowing through the first load port 104, the positive direction is the flow rate of the gas flowing from the supply port 102 side toward the first load port 104, and the negative direction is the first load port. The flow rate of the gas flowing from 104 toward the exhaust port 106. The horizontal axis represents the pendulum angle θ of the pendulum 12 and the position of the spool 56 in the X direction corresponding to the pendulum angle θ.

That is, the first load port 92 overlaps the first land 60 is a state which is open portion toward the exhaust port 94 when the neutral position, the spool 56 is moved driven to X = X ₁₁ Thus, the first load port 92 is once completely shielded by the first land 60. And the shielding state continues until it is further displaced in the X direction to some extent. If the shielding state continues until X = X ₁₂ , the output state of the first load port 104 connected to the first load port 92 does not change during ΔX ₁ = (X ₁₂ −X ₁₁ ). If ΔX ₁ is referred to as a dead zone displacement amount at the first load port 104, the first load port 104 is not displaced until X = X ₁₁ to X = X ₁₂ which is a position exceeding the dead zone displacement amount ΔX _1. Is the first control gas pressure P _C1 .

This will be described in relation to the pendulum angle θ of the pendulum 12 as follows. That is, when the pendulum 12 is in the neutral position, the first load port 104 communicates with the exhaust port 106, so the gas pressure at the first load port 104 is atmospheric pressure. When the pendulum 12 is rotated from theta = 0 the neutral position to theta = theta _11, the first load port 92 is temporarily blocked by the first land 60. θ ₁₁ is a rotation angle corresponding to X ₁₁ . Therefore, the amount of θ ₁₁ is determined by setting the axial length of the opening portion between the first land 60 and the first load port 92 in the neutral position. The larger the value of the axial length of the opening at the neutral position, the larger θ ₁₁ becomes.

Until the rotating pendulum 12 is further theta = theta _12, the gas pressure of the first load port 104 is not changed. In other words, even if the change from the rotation theta = theta ₁₁ of the pendulum 12 to theta = theta _12, the gas pressure of the first load port 104 is not changed. In that sense, Δθ ₁ = (θ ₁₂ −θ ₁₁ ) during this period can be called a dead zone pendulum angle at which the gas pressure of the first load port 104 does not change with respect to the rotation of the pendulum 12. Δθ ₁ corresponds to ΔX ₁ . Therefore, the magnitude of Δθ ₁ is determined by setting the value of the difference between the axial length of the first land 60 and the axial length of the first load port 92. As the value of {(length in the axial direction of the first land 60) − (length in the axial direction of the first load port 92)} increases, the dead band pendulum angle Δθ ₁ increases.

Therefore, when the pendulum 12 is rotated from theta = theta ₁₁ to theta = theta ₁₂ beyond the dead zone pendulum angle [Delta] [theta] _1, the gas pressure of the first load port 104 is controlled gas pressure P _C1. In FIG. 3, the gas flow at that time is changed from the first supply port 102 to the first supply port 90, and from the first supply port 90 to the stem between the first end land 58 and the first land 60. An arrow heading from the first load port 92 to the first load port 104 is shown to the first load port 92.

  When the spring seats 70 and 72 are driven to move in the X direction from the neutral position, the second load port 108 is always in communication with the exhaust port 106. This is indicated by a bidirectional arrow between the second load port 108 and the exhaust port 106 in FIG. This arrow simply indicates communication. Since the state of the second load port 108 originally communicated with the exhaust port, the gas is sent from the second load port 108 to the exhaust port 106 simply because the spring seats 70 and 72 are driven to move in the X direction from the neutral position. It doesn't start to flow.

Thus, the pendulum angle theta is increased from the neutral state, the first load port 104 from theta = 0 to theta = theta ₁₁ communicates with the exhaust port 106. Therefore, during this time, the first load port 104 is in an exhaust state. During the period of the dead band pendulum angle Δθ ₁ from θ = θ ₁₁ to θ = θ ₁₂ , the first load port 104 is in a shielding state. When more than theta = theta _12, the first load port 104 communicates with the supply port 102, the control gas pressure is generated. Accordingly, the first pendulum angle theta is turned theta ₁₂ or more, the first load port 104, so that the control gas pressure for the body tilt is supplied.

If pendulum angle theta decreases the theta from ₁₂ or more states theta, the gas does not flow to the first load port 104 with a pendulum angle theta = theta _12. However, during the period of the dead band pendulum angle Δθ ₁ from the pendulum angle θ = θ ₁₂ to θ ₁₁ , the first load port 104 is in a shielding state and does not enter an exhaust state. The exhaust state is reached when the dead zone pendulum angle Δθ ₁ is exceeded and θ = θ ₁₁ is reached. Thus, the period of the dead zone pendulum angle Δθ ₁ is also a hysteresis period. That is, when the pendulum angle theta is increased does not supply gas to the first load port 104 from the supply port 102 to the θ = θ _12. Further, when the pendulum angle theta is decreased, not the first load port 104 to theta = theta ₁₁ to exhaust state.

Therefore, by appropriately setting the size of the dead band pendulum angle Δθ ₁ , even if there is vibration noise or the like, gas can be reliably and stably supplied from the supply port 102 to the first load port 104. The load port 104 can be reliably discharged into a discharged state. Thus, the size of the dead zone pendulum angle Δθ ₁ can be set in consideration of the magnitude of vibration noise, the control margin for vehicle body control, and the like.

In FIG. 3, the case where the pendulum angle θ swings counterclockwise on the paper surface and the position X of the spool 56 moves from the right side to the left side on the paper surface has been described. Since the spool / sleeve mechanism 50 has a symmetrical structure, the pendulum angle θ is swung clockwise on the paper surface, and the position X of the spool 56 moves from the left side to the right side on the paper surface. The same operation is performed only by reversing the moving direction of 3. In FIG. 4, Q ₁ is replaced with Q ₂ .

Of course, the structure of the spool / sleeve mechanism 50 may not be symmetrical. In this case, the first load port 104 may be different from θ ₁₁ , θ ₁₂ , Δθ ₁ , X ₁₁ , X ₁₂ , ΔX _1. In addition, respective values for the second load port 108 can be set. For example, a dead zone displacement amount ΔX ₂ different from the dead zone displacement amount ΔX ₁ of the first load port 104 can be set for the second load port 108. As described above, when the dead band displacement amount is made different between the first load port 104 and the second load port 108, these can be distinguished, and the former can be referred to as a first dead band displacement amount and the latter can be referred to as a second dead band displacement amount. .

Upon setting of the dead band pendulum angle [Delta] [theta] _1, it should be considered, and the influence of free vibration of the pendulum 14, a noise vibration N _A of the housing portion 14 is subjected.

A pendulum damper 30 is provided to suppress free vibration of the pendulum 14. As described for the pendulum damper 30, by appropriately setting the aperture 44, the sensitivity of the pendulum angle θ to the noise vibration N _A can be reduced, and free vibration of the pendulum 12 can be suppressed.

Further, in order to suppress the influence of noise vibration N _A, the spool sleeve mechanism 50, the spring portion and the damper portion is provided. As described with reference to FIG. 2, the pendulum movement of the pendulum 12 is converted into the straight movement of the spring seats 70 and 72 by the sphere 52. The rectilinear motion of the spring seats 70 and 72 is transmitted to the spool 56. At this time, the spring seats 70 and 72 do not directly drive the spool 56 but drive it using the spring portion, and the damper portion moves the motion. Suppress. The spring portion is provided between the spring seats 70 and 72 and the spool 56, and the damper portion is provided between the spool 56 and the sleeve 54. With respect to the axial displacement of the spool, the spring portion gives an elastic force having a predetermined spring constant, and the damper portion gives a damping force having a predetermined damping constant. Therefore, the pendulum motion of the pendulum 12 is applied to the spool 56 under a damping vibration system determined by a predetermined spring constant k of the spring part, a predetermined damping constant c of the damper part, and a mass m including the pendulum 12 and the spool 56. Will be communicated.

  FIG. 5 is a diagram illustrating a vibration model of the control valve 10 using a pendulum angle including a spring portion and a damper portion. Here, the first coil spring 76 and the second coil spring 78 are combined into one spring model having a spring constant k, and the first gas space 80 and the second gas space 82 are combined into a damper model having a damping constant c. The mass of the system from the pendulum 12 to the spool 56 is collectively shown as a model in which the mass m is concentrated on the pendulum 12. Thus, the mass of the spool 56 is set to be a very small value with respect to the mass of the pendulum 12.

Suppression of noise vibration N _A can be carried out in damped oscillation system of FIG. 5, the relationship between the spring constant k and the damping constant c and the mass m by appropriately setting.

  The control valve using the pendulum angle according to the present invention can be used for tilt control of a railway vehicle.

  10 control valve using pendulum angle, 12 pendulum, 14 housing, 16 center of rotation, 20 connecting shaft, 22 pendulum side arm, 24 center disc, 26 spool side arm, 30 pendulum damper, 32, 52 sphere, 33 cylinder 34, damper housing, 36 moving body, 38, 40 damper space, 42, 84, 100 communication path, 44, 86 throttle, 50 spool / sleeve mechanism, 54 sleeve, 56 spool, 58, 64 end land, 60 1st land, 62 2nd land, 70, 72 Spring seat, 76 1st coil spring, 78 2nd coil spring, 80 1st gas space, 82 2nd gas space, 90 1st supply port, 92 1st load port, 94 exhaust port, 96 second load port, 98 second supply port, 102 first supply port, 104 first load port, 106 exhaust port, 1 08 Second load port, 110 Second supply port.

Claims (3)

A pendulum that performs a pendulum motion around a predetermined rotation center in response to acceleration;
A spool driven according to the pendulum angle of the pendulum and provided with a first land and a second land along the axial direction of the stem;
A supply port for supplying a gas having a supply gas pressure, a first load port and a second load port provided corresponding to the first land and the second land, and exhausting to the outside. A sleeve having an exhaust port;
A spring portion that gives an elastic force having a predetermined spring constant with respect to the axial displacement of the spool;
A damper portion that applies a damping force having a predetermined damping constant to the axial displacement of the spool;
A pendulum damper that suppresses the free vibration of the pendulum,
A control valve using a pendulum angle. In the control valve using the pendulum angle according to claim 1,
When the spool is in a neutral position with respect to the sleeve, both the first load port and the second load port are in a positional relationship communicating with the exhaust port, and from the neutral position to the second load port side of the sleeve according to the pendulum angle. When the spool is displaced toward the first position, the first load port is temporarily shut off by the first land, and further displaced beyond a predetermined first dead zone displacement amount so that the first load port becomes the supply port. When the spool is displaced from the neutral position toward the first load port side of the sleeve in accordance with the pendulum angle, the second load port is temporarily shut off by the second land and then further predetermined. The pendulum angle is characterized in that the second load port communicates with the supply port by a predetermined displacement exceeding the second dead zone displacement amount. Control valve used. In the control valve using the pendulum angle according to claim 1,
The center of rotation of the pendulum provided in the housing including the sleeve;
A spool side tip provided integrally with the pendulum on the opposite side of the pendulum across the center of rotation of the pendulum;
A spring seat provided at the spool side tip,
With
The spring portion includes a first coil spring provided between the end portion on the first land side of the spool and the spring seat, and a second coil spring provided between the end portion on the second land side of the spool and the spring seat,
The damper portion includes a first gas space between an end portion on the first land side of the spool and an inner wall of the end portion on the first load port side of the sleeve, an end portion on the second land side of the spool, and a second load of the sleeve. A control valve using a pendulum angle, wherein the second gas space between the end side inner wall of the port side and the second gas space communicates with each other through a communication path through a throttle portion.

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