WO2010010810A1 - Air spring device - Google Patents

Air spring device Download PDF

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Publication number
WO2010010810A1
WO2010010810A1 PCT/JP2009/062361 JP2009062361W WO2010010810A1 WO 2010010810 A1 WO2010010810 A1 WO 2010010810A1 JP 2009062361 W JP2009062361 W JP 2009062361W WO 2010010810 A1 WO2010010810 A1 WO 2010010810A1
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WO
WIPO (PCT)
Prior art keywords
air spring
spring means
shear
surface plate
liquid
Prior art date
Application number
PCT/JP2009/062361
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French (fr)
Japanese (ja)
Inventor
玲 東谷
Original Assignee
株式会社ブリヂストン
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Publication of WO2010010810A1 publication Critical patent/WO2010010810A1/en

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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B61—RAILWAYS
    • B61F—RAIL VEHICLE SUSPENSIONS, e.g. UNDERFRAMES, BOGIES OR ARRANGEMENTS OF WHEEL AXLES; RAIL VEHICLES FOR USE ON TRACKS OF DIFFERENT WIDTH; PREVENTING DERAILING OF RAIL VEHICLES; WHEEL GUARDS, OBSTRUCTION REMOVERS OR THE LIKE FOR RAIL VEHICLES
    • B61F5/00—Constructional details of bogies; Connections between bogies and vehicle underframes; Arrangements or devices for adjusting or allowing self-adjustment of wheel axles or bogies when rounding curves
    • B61F5/02—Arrangements permitting limited transverse relative movements between vehicle underframe or bolster and bogie; Connections between underframes and bogies
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F13/00—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs
    • F16F13/002—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising at least one fluid spring
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F13/00—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs
    • F16F13/04—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper
    • F16F13/06—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper the damper being a fluid damper, e.g. the plastics spring not forming a part of the wall of the fluid chamber of the damper
    • F16F13/08—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper the damper being a fluid damper, e.g. the plastics spring not forming a part of the wall of the fluid chamber of the damper the plastics spring forming at least a part of the wall of the fluid chamber of the damper
    • F16F13/10—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper the damper being a fluid damper, e.g. the plastics spring not forming a part of the wall of the fluid chamber of the damper the plastics spring forming at least a part of the wall of the fluid chamber of the damper the wall being at least in part formed by a flexible membrane or the like
    • F16F13/108—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper the damper being a fluid damper, e.g. the plastics spring not forming a part of the wall of the fluid chamber of the damper the plastics spring forming at least a part of the wall of the fluid chamber of the damper the wall being at least in part formed by a flexible membrane or the like characterised by features of plastics springs, e.g. attachment arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/02—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems
    • F16F15/022—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using dampers and springs in combination
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
    • F16F9/02—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium using gas only or vacuum
    • F16F9/04—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium using gas only or vacuum in a chamber with a flexible wall

Definitions

  • the present invention is an air spring device suitable for use in a railway vehicle, comprising an air spring and a vertical input shear spring means, and more particularly a vibration damping function associated with the flow of pressurized gas enclosed in the air spring.
  • the present invention relates to an air spring device that can also exhibit a vibration damping function that accompanies the flow of liquid, and effectively increases the spring constant in the vertical direction even when the railway vehicle runs under conditions where the vibration frequency increases. This is to propose a technology that can ensure a sufficient vibration damping function while preventing it.
  • This includes an outer cylinder and an inner cylinder, a diaphragm provided over both of them, a support member having a conical or pyramidal outer peripheral surface, and an outer peripheral surface of the support member and the inner cylinder.
  • the elastic deformation of the elastic member due to the movement is configured to be started after the elastic body is elastically deformed by a predetermined amount.
  • a buffer body made of an elastic member is arranged between the support member and the inner cylinder, and the elastic member is elastically deformed by a predetermined amount due to the relative movement of the inner cylinder and the support member. It is configured to start after that. For this reason, when the load acting on the outer cylinder becomes larger than a predetermined value, in addition to the elasticity of the elastic body, the elasticity of the buffer body is added in parallel, and the spring constant can be increased without difficulty. This makes it possible to achieve a soft spring characteristic with a small spring constant up to a certain load, and to switch to a state with a hard spring characteristic with a large spring constant when a large load is applied.
  • the annular elastic body provided over the outer peripheral surface of the support member and the inner cylinder is softened during normal normal operation.
  • the elastic body is made of laminated rubber, the support member and the inner cylinder can be stably elastically supported with each other.
  • the mounting boss portion provided on the upper surface plate, the lower surface plate through-hole, etc. function as a flow passage restriction portion, and the flow passage restriction portion is used as a large-capacity auxiliary tank, an air chamber, etc. Because of the so-called diffusion attenuation based on the sudden expansion of the flow path when the pressurized air flows between the air spring and the auxiliary tank etc. In order to ensure the above, a gas damping function against low frequency vibrations of about 1 to 2 Hz is provided.
  • Patent Document 2 states that “the basic configuration is an air spring, and the first liquid chamber and the second liquid chamber communicating with each other can be combined to absorb vibration in any direction and support.
  • the spring constant can be kept small regardless of the magnitude of the load, and if the diameter and length of the orifice are set according to the frequency, the damping force proportional to the support load is applied to both the low frequency range and the high frequency range.
  • a liquid-filled air spring suitable as an anti-vibration support for an engine is described, and for this reason, “a pair of two opposing substrates is disposed along an axis perpendicular to the substrate.
  • the liquid chamber has an orifice It is set to be adopted and a vibration damping function and a second fluid chamber in contact with the first liquid chamber and the air chamber in contact with one of the substrates by a partition plate.
  • the air spring described in Patent Document 2 is, for example, “The static load generated when the engine is mounted pressurizes the gas in the air chamber using the liquid that fills the upper substrate and the liquid chamber as a transmission medium, and the upper substrate is a gas
  • the vertical component of the vibration generated by driving the engine is significantly higher than that of the pressurized gas in the air chamber. Therefore, it is transmitted to the pressurized gas through the liquid and absorbed mainly by the elastic deformation of the pressurized gas, and the liquid attenuates the vibration due to the frictional resistance when moving between the liquid chambers through the orifice.
  • the air spring is used for damping the vibration because the liquid flows between the two liquid chambers through the orifice regardless of the vibration frequency. To outside Be attached the bumpers is not required.
  • JP 2006-329280 A Japanese Patent Laid-Open No. 11-101287
  • the object of the present invention is to solve such problems of the prior art, and the object of the present invention is to sufficiently absorb the low-frequency vibration of the vehicle with excellent responsiveness.
  • an air spring device that can dampen the vibration under the action of the liquid attenuating means against high frequency vibration that can be damped together with the flow restriction of the air spring.
  • the air spring device of the present invention comprises an upper plate and a lower plate, and a cylindrical flexible film body in which the respective end portions are airtightly connected to the respective face plates, and the inside thereof is pressurized at or above atmospheric pressure.
  • An air spring formed by enclosing gas, and a shear spring means mainly composed of rubber, which is disposed on the upper surface plate side or the lower surface plate side of the air spring and is mainly subjected to shear deformation by a vertically downward input.
  • the air spring is provided with a gas damping mechanism for the vertical input
  • the shear spring means is provided with a liquid damping means for damping the vertical input independently of the gas damping mechanism. It will be.
  • the gas attenuating mechanism is composed of a pressurized gas storage container connected to the upper surface plate or the lower surface plate, and a flow path restricting portion provided at the upper surface plate or the lower surface plate, or an intermediate portion reaching the gas storage container. can do.
  • the liquid attenuating means is formed by a partition member of a liquid chamber that is partitioned by a recess provided in the shear spring means and a diaphragm independent of the air spring that closes the opening of the recess when the liquid is sealed. It is preferable that the divided liquid chambers to be divided are connected to each other by a throttle passage provided outside the liquid chamber or outside the liquid chamber.
  • the air spring and the shear spring means are preferably arranged in series with respect to the input in the vertical direction, and the compression mainly composed of rubber that is mainly compressed and deformed by the input in the vertical direction downward.
  • spring means are also provided.
  • the compression spring means and the shear spring means are preferably arranged in series with respect to the vertical input.
  • the shear spring means can generate only a shearing force, but it is composed of a truncated cone-shaped or truncated pyramidal frustum-shaped rubber member and a cone that contributes to suppressing deformation of the rubber member.
  • the laminated body of the alternate structure with the trapezoidal rigid plate is a joined structure to the core body and the outer cylinder, by causing a shear deformation accompanied by a compressive deformation or the like to the downward input in the vertical direction, While ensuring the durability of the rubber member, the magnitude of the generated spring force can be easily adjusted under the selection of the respective taper angles.
  • the compression spring means may be a structure in which an alternate laminated body of an annular rubber plate and an annular rigid plate is joined to the lower end support plate and the upper end ring, and a required spring force in the compression direction. It is preferable to secure the occurrence of the small shear spring force in the horizontal direction.
  • the elastic deformation of the air spring and the shear spring means mainly against vibrations in the vertical direction and low-frequency natural vibrations of about 1 to 2 Hz during normal running of a railway vehicle.
  • vibration can be effectively absorbed under excellent responsiveness, and the compressed gas can flow between the air spring and the gas storage container under the action of the gas damping mechanism.
  • the vibration can be effectively damped by so-called diffusion attenuation by flowing through the part, energy absorption based on frictional resistance or the like exerted on the pressurized gas by the flow path restricting part, and the like.
  • the vehicle is vibrated at a frequency exceeding 10 Hz due to the vehicle entering the tunnel or the like at high speed, and the flow restrictor of the air spring becomes clogged.
  • the liquid damping device provided independently of the air spring can exhibit a sufficient vibration damping function by tuning, so that the entire air spring device In other words, without excessively increasing the spring force, the vibration damping function based on the flow of the liquid in the liquid damping device can be effectively exhibited while sufficiently securing the riding comfort of the vehicle.
  • the gas damping mechanism and the liquid damping means are provided independently of each other, and each of them functions separately without mutual influence, thereby reducing the low frequency vibration of the vehicle. It can absorb and dampen well under high responsiveness, and the high-frequency vibration that clogs the flow restrictor of the gas damping mechanism Can be effectively attenuated. It should be noted that such a vibration damping function can be similarly exerted even when the air spring is deflated by puncture or the like.
  • the gas damping mechanism is connected to the upper surface plate or the lower surface plate, and the pressurized gas storage container, and the upper surface plate or the lower surface plate, or the flow restrictor provided in the intermediate portion leading to the gas storage container.
  • a required gas damping mechanism can be configured without making a major change to a conventional air spring having a vibration damping function.
  • the liquid damping means completely independent from the gas damping mechanism can be configured very compactly. This is more effective when the throttle passage is provided in the liquid chamber.
  • the degree of freedom in selecting the throttle passage length can be increased, and the required liquid column resonance frequency contributing to vibration damping can be easily realized. A sufficiently long path can be secured to increase the vibration damping capability due to frictional resistance.
  • the air spring and the shear spring means are arranged in series with respect to the input in the vertical direction, the performance of the smaller spring constant is manifested by the principle of the series spring, and the vertical vibration of the vehicle Can be elastically supported and damped.
  • the compression spring means mainly composed of rubber which is mainly compressed and deformed by the downward input in the vertical direction
  • the compression is performed.
  • the vibration elastically under the hard spring characteristics of the spring means it is possible to ensure the running stability of the vehicle. This is because the air spring is deflated by puncture etc. and exhibits its original function.
  • the vertical input is elastically supported by both the shear spring means and the compression spring means after it is not obtained.
  • the force When a horizontal force is input to such an air spring device, the force can be flexibly elastically supported mainly by the horizontal deformation of the air spring and the shear deformation of the compression spring means. it can.
  • Such elastic support of the horizontal input by the compression spring means is mainly applied to the magnitude of the vertical load under the manifestation of the shear spring characteristics of the compression spring, regardless of the presence or absence of the deflate of the air spring. Regardless, it will be flexible enough.
  • the shear spring means receives a vertical downward input large enough to deform to its deformation limit, and the subsequent elastic support of the vertical downward input is performed exclusively by the action of the compression spring means. Even if it becomes, it can be elastically supported flexibly with the shearing deformation of the compression spring means regardless of whether the air spring is deflated or not for the input in the horizontal direction.
  • the shear spring means is a joined structure to the core body and the outer cylinder, which can be the inner cylinder, of the alternately laminated body of the frustum-shaped rubber member and the frustum-shaped rigid plate, Compared to a case where the rubber member is deformed in the compression direction in addition to the shearing direction in response to the vertical downward input, the rubber member is subjected to only the shear deformation under a tendency of increasing the spring constant. Since the absolute deformation amount of the member can be suppressed, the durability of the rubber member can be increased. On the other hand, the shear spring means can contribute to the exertion of the elastic function even with respect to the horizontal input. it can.
  • the compression spring means may be joined to, for example, a horizontal lower end support plate, which is an alternating laminate of annular rubber plates and annular rigid plates, both horizontally, also to the horizontal upper ring.
  • a horizontal lower end support plate which is an alternating laminate of annular rubber plates and annular rigid plates, both horizontally, also to the horizontal upper ring.
  • each of the shear spring means and the compression spring means is sequentially arranged from the air spring side and they are arranged in series with respect to the vertical input, for example, the elasticity of the vertically downward input
  • the above-mentioned various functions can be sufficiently exerted with a device having a simple structure.
  • the compression spring means functions sufficiently smoothly and reliably for the elastic support of the horizontal input. be able to.
  • the core body of the shearing spring means which can be the inner cylinder
  • the core body of the shearing spring means which can be the inner cylinder
  • the compression spring means for example, into the hollow part in relation to the dimension of the hollow part of the compression spring means. It is possible to arrange a part of the shearing spring means so that the space occupied by the apparatus, and thus the outer dimensions can be reduced, and the floor of the railway vehicle can be reduced. it can.
  • FIG. 1 is a longitudinal sectional view showing an embodiment of the present invention.
  • 1 is an upper surface plate attached to the vehicle body side, for example, in a horizontal posture
  • 2 is a lower surface plate
  • 3 is both surfaces thereof.
  • the ends of the plates 1 and 2 are hermetically connected to each other.
  • the cylindrical flexible film bodies having a self-sealing structure are shown.
  • These members 1, 2 and 3 are internally provided with air, inert gas, etc.
  • the air spring 4 is configured by enclosing a gas having a predetermined pressure.
  • a boss 5 as a flow passage restricting portion is provided on the upper surface plate 1 of the air spring 4, and the air spring 4 is communicated with a pressurized gas storage container (not shown) via the boss 5.
  • the storage container and the boss 5 constitute a gas damping mechanism for vertical input.
  • this gas damping mechanism the dimensions of the boss 5 and the like are tuned so as to attenuate low frequency vibrations of about 1 to 2 Hz, with the primary aim of ensuring riding comfort on a railway vehicle or the like.
  • the shear spring means 6 and the compression spring means 7 are arranged in series on the lower surface plate 2 side of the air spring 4, and the air spring 4, the shear spring means 6, the compression spring means 7, and the like. Are sequentially arranged in series. This results in a soft spring identification that reveals the performance of the lower spring constant for vertical input. Note that the shear spring means 6 and the compression spring means 7 can be arranged in a different order from that shown in the figure.
  • the shear spring means 6 mainly composed of rubber, which is mainly shear-deformed by a downward input in the vertical direction, has a truncated cone shape and a pyramid whose dimensions gradually increase toward the lower side of the figure.
  • the compression spring means 7 mainly composed of rubber, which is mainly compressed and deformed by the downward input in the vertical direction, is located on the lower side of the lower surface plate 2 and is attached to the carriage in a horizontal posture, for example.
  • the annular horizontal rubber plate 7a and the annular rigid plate 7b joined to the lower end support plate 9a to the lower end support plate 9a and the upper end ring 9b.
  • the inner diameters of the rubber plate 7a, the rigid plate 7b, and the upper end ring 9b are made uniform.
  • Each of the spring means 6, 7 arranged as shown in the figure below the lower surface plate 2 of the air spring 4 is here one for attaching the outer cylinder 8 b of the shear spring means 6 to the lower surface side of the lower surface plate 2. Then, the lower end portion of the core body 8a is inserted into the hollow portion 7c of the compression spring means 7 via the flange member 10 engaged with the upper end ring 9b of the compression spring means 7, and the core body 8a It is possible to attach the lower end to the air spring 4 by assembling the lower ends so as to be positioned away from the lower end support plate 9a so as not to contact the lower end support plate 9a even after the compression spring means 7 is compressed and deformed. it can. In this way, the core material 8a of the shear spring means 6 is placed in the hollow portion 7c of the compression spring means 7 so that the entire apparatus can be reduced in size.
  • the deformation of the rubber member 6a located on the innermost circumferential side of the shearing spring means 6 due to shear deformation or the like caused by the downward downward input in the vertical direction is the frustum-shaped rigidity located on the innermost circumferential side.
  • the plate 6b is prevented from coming into contact with the flange member 10, and further shear deformation of the shear spring means 6, and further subsequent downward displacement of the lower face plate 2, causes the action of the liquid damping means described later. Will be performed under.
  • reference numerals 1a and 2a denote sliding plates provided on the lower surface of the upper surface plate 1 and the upper surface of the lower surface plate 2, respectively, for example, a stainless steel plate and a polytetrafluoroethylene plate, respectively.
  • These slidable contact plates 1a and 2a are formed when the double-sided plates 1 and 2 come into contact with each other due to the action of a large vertical load or the deflation of the air spring 4 or the like. It functions to make the sliding displacement in a horizontal plane sufficiently smooth.
  • the shear spring means 6 is provided with the liquid attenuating means 11 that causes the attenuation of the input in the vertical direction completely independently of the gas attenuating mechanism.
  • the liquid damping means 11 shown in the figure is a rigid partition of a liquid chamber 14 formed by a recess 12 formed at the top of the shearing spring means 6 and a diaphragm 13 that closes the opening of the recess 12 under liquid filling.
  • Each of the divided liquid chambers 14a and 14b divided by the member 15 is configured to communicate with each other by, for example, a throttle passage 16 provided in the liquid chamber 14, where the outer surface side of the diaphragm 13 is Open to the atmosphere.
  • the gas damping mechanism on the air spring side cannot exhibit the vibration damping function due to, for example, the clogging phenomenon of the boss 5 as the flow path restricting portion.
  • the spring of the air spring 4 When the constant is forced to increase or when the air spring 4 is deflated by puncture or the like, the shear spring means 6 is deformed downward in the vertical direction.
  • the liquid in the liquid chamber 14a flows into the upper divided liquid chamber 14b through the throttle passage 16, so that the internal pressures of both the liquid chambers 14a and 14b are brought into an equilibrium state.
  • the liquid damping means 11 is tuned so as to function effectively with respect to high-frequency vibrations in a certain region, and vibrations having a lower frequency than the vibrations in that region are normally attenuated by the flow restrictor of the air spring 4. It will be sufficiently damped by the mechanism.
  • the air spring 4, the shear spring means 6, and the compression spring means 7 are configured to be arranged in series with respect to the input in the vertical direction, and the gas damping mechanism and the gas damping mechanism are
  • this air spring device provided with the independent liquid damping mechanism 11 is applied to, for example, a bolsterless bogie for a railway vehicle, it is generally used under various selections according to requirements. Therefore, it is possible to sufficiently cope with vibrations up to about ⁇ 40 mm in the vertical and horizontal directions, and to sufficiently absorb a large displacement of about 150 mm in the front-rear direction. In this case, vibrations in the vertical and horizontal directions are absorbed by the air spring 4, and displacement in the front and rear direction is absorbed by the air spring 4 and the compression spring means 7.
  • the vertical vibration is caused by the shear spring means 6 based on the seating of the top plate 1 etc. on the shear spring means 6, and the horizontal vibration is The large displacement in the front-rear direction is absorbed by the sliding displacement based on the action of the sliding contact plates 1a, 2a.
  • the low frequency vibration in the vertical direction is damped by the flow of pressurized gas through the boss 5 by the gas damping mechanism that is tuned to a low frequency frequency of about 1 to 2 Hz in order to ensure vibration riding comfort. Will be.
  • the apparatus receives high frequency vibration of about 10 to 20 Hz, for example, and the gas damping mechanism cannot perform the intended damping function, and the spring constant of the air spring 4 increases, the shear spring is used. Since the vibration is attenuated under the action of the liquid attenuating means 11 accompanying the shear deformation of the means 6, it is possible to ensure a comfortable ride on the vehicle or the like.
  • the vibration damping function of the liquid damping means 11 can be exhibited even when the air spring 4 is deflated by puncture or the like, the liquid damping is performed even when the air spring 4 becomes inoperable. With the means 11, it is possible to effectively exhibit the vibration proof and damping ability.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Acoustics & Sound (AREA)
  • Aviation & Aerospace Engineering (AREA)
  • Fluid-Damping Devices (AREA)
  • Vibration Prevention Devices (AREA)
  • Combined Devices Of Dampers And Springs (AREA)

Abstract

An air spring device comprising an air spring (4) and a shear spring means (6).  The air spring (4) is provided with an upper surface plate (1), a lower surface plate (2), and a tubular flexible film body (3) having opposite ends respectively air-tightly connected to the surface plates (1, 2), and the air spring (4) has sealed therein a pressurized gas having a pressure higher than or equal to the atmospheric pressure.  The shear spring means (6) is mounted on the lower surface plate side of the air spring (4) and is mainly subjected to shear deformation due to a vertical input.  The air spring (4) is also provided with a gas damping mechanism for damping a vertical input.  A liquid damping means (11) for damping the vertical input independently of the gas damping is provided in the shear spring means.

Description

空気ばね装置Air spring device
　この発明は、空気ばねと、垂直入力剪断ばね手段とを具える、鉄道用車両に用いて好適な空気ばね装置、とくには、空気ばね内に封入した加圧気体の流動に伴う振動減衰機能の他、液体の流動に伴う振動減衰機能をも発揮できる空気ばね装置に関するものであり、鉄道車両が、振動周波数が高くなる条件の下を走行してなお、垂直方向のばね定数の増加を有効に防止しつつ、十分な振動減衰機能の発揮を担保できる技術を提案するものである。 The present invention is an air spring device suitable for use in a railway vehicle, comprising an air spring and a vertical input shear spring means, and more particularly a vibration damping function associated with the flow of pressurized gas enclosed in the air spring. In addition, the present invention relates to an air spring device that can also exhibit a vibration damping function that accompanies the flow of liquid, and effectively increases the spring constant in the vertical direction even when the railway vehicle runs under conditions where the vibration frequency increases. This is to propose a technology that can ensure a sufficient vibration damping function while preventing it.
　上面板および下面板と、これらのそれぞれの面板に、それぞれの端部を気密に連結した筒状可撓膜体とからなり、内部に、大気圧以上の加圧気体、たとえば加圧空気を封入してなる空気ばねと、この空気ばねの上面板側もしくは下面板側に配設されて、垂直方向の入力によって主には剪断変形される、ゴムを主体とする剪断ばね手段、たとえば円錐台状ばね手段とを具える空気ばね装置としては、特許文献１に記載されたものがある。 It consists of a top and bottom plate, and a cylindrical flexible film body with each end face connected to each of these face plates in an airtight manner, and a pressurized gas above atmospheric pressure, such as pressurized air, is enclosed inside And an air spring formed on the top plate or the bottom plate of the air spring, and a shear spring means mainly composed of rubber, which is mainly subjected to shear deformation by vertical input, for example, a truncated cone shape As an air spring device including spring means, there is one described in Patent Document 1.
　これは、外筒および内筒と、これら両者に亘って配備されるダイヤフラムと、円錐面又は角錐面状の外周面を有する支持部材と、この支持部材の外周面と前記内筒とに亘って配備される環状の弾性体とを有して成る空気ばねにおいて、弾性部材を有する緩衝体を前記内筒と前記支持部材との間に配備して、前記内筒と前記支持部材との相対接近移動による前記弾性部材の弾性変形が、前記弾性体が所定量弾性変形してから開始される状態に構成したものである。 This includes an outer cylinder and an inner cylinder, a diaphragm provided over both of them, a support member having a conical or pyramidal outer peripheral surface, and an outer peripheral surface of the support member and the inner cylinder. An air spring having an annular elastic body to be deployed, wherein a shock absorber having an elastic member is disposed between the inner cylinder and the support member, so that the inner cylinder and the support member are relatively close to each other. The elastic deformation of the elastic member due to the movement is configured to be started after the elastic body is elastically deformed by a predetermined amount.
　この空気ばねは、支持部材と内筒との間に弾性部材から成る緩衝体を配置して、内筒と支持部材との相対接近移動による弾性部材の弾性変形が、弾性体が所定量弾性変形してから開始される状態に構成されている。このため、外筒に作用する荷重が所定以上に大きくなると、弾性体による弾性に加えて緩衝体による弾性が並列的に加算されることになり、ばね定数を無理なく大きくすることができる。これにより、ある程度の荷重までは小さいばね定数による柔らかいばね特性を持つ状態にできるとともに、大荷重が作用する場合には大きいばね定数による硬いばね特性を持つ状態に切換えることが可能になる。
　その結果、円錐台又は角錐台状の外周面を持つ支持部材を有する空気ばねにおいて、支持部材の外周面と内筒とに亘って配備される環状の弾性体を、通常の正常動作時における柔らかいばね特性を持つものとしながらも、大荷重時には全体として硬いばね特性が発揮できて腰のあるものとなるよう、非線形特性が備わったものに改善することができた。この場合、弾性体を積層ゴムで構成すれば、支持部材と内筒とが互いに安定的に弾性支持されるようにすることができると、するものである。 In this air spring, a buffer body made of an elastic member is arranged between the support member and the inner cylinder, and the elastic member is elastically deformed by a predetermined amount due to the relative movement of the inner cylinder and the support member. It is configured to start after that. For this reason, when the load acting on the outer cylinder becomes larger than a predetermined value, in addition to the elasticity of the elastic body, the elasticity of the buffer body is added in parallel, and the spring constant can be increased without difficulty. This makes it possible to achieve a soft spring characteristic with a small spring constant up to a certain load, and to switch to a state with a hard spring characteristic with a large spring constant when a large load is applied.
As a result, in an air spring having a support member having a frustoconical or truncated pyramid-shaped outer peripheral surface, the annular elastic body provided over the outer peripheral surface of the support member and the inner cylinder is softened during normal normal operation. Although it has spring characteristics, it can be improved to have non-linear characteristics so that it can exhibit firm spring characteristics as a whole at a heavy load and has a waist. In this case, if the elastic body is made of laminated rubber, the support member and the inner cylinder can be stably elastically supported with each other.
　ところで、従来の一般的な空気ばねでは、上面板に設けた取付けボス部、下面板貫通孔等を流路絞り部として機能させ、その流路絞り部を、大容積の補助タンク、空気室等に連通させて、空気ばねと補助タンク等との間での加圧空気の流動に際する、流路の急拡大に基く、いわゆる拡散減衰等によって、多くは、鉄道車両等への乗心地性を確保するべく、１～２Ｈｚ程度の低周波振動に対する気体減衰機能をもたらすこととしている。これに対し、特許文献１に記載された空気ばねでは、ダイアフラムに囲まれる空気ばねの内容積が大きいことから、低周波振動を減衰させる目的の下で、空気ばねに補助タンク等を取り付けると、空気ばねのトータル容積が大きくなりすぎて、垂直方向の入力に対するばね定数が小さくなりすぎ、所要の振動吸収機能さえも発揮できなくなる。このため、振動減衰の実現のためには、外部ダンパーを別途付設することが必要になるという、装置コスト上、ならびに、装置寸法上の問題があった。 By the way, in the conventional general air spring, the mounting boss portion provided on the upper surface plate, the lower surface plate through-hole, etc. function as a flow passage restriction portion, and the flow passage restriction portion is used as a large-capacity auxiliary tank, an air chamber, etc. Because of the so-called diffusion attenuation based on the sudden expansion of the flow path when the pressurized air flows between the air spring and the auxiliary tank etc. In order to ensure the above, a gas damping function against low frequency vibrations of about 1 to 2 Hz is provided. On the other hand, in the air spring described in Patent Document 1, since the inner volume of the air spring surrounded by the diaphragm is large, when an auxiliary tank or the like is attached to the air spring for the purpose of attenuating low frequency vibration, Since the total volume of the air spring becomes too large, the spring constant with respect to the input in the vertical direction becomes too small, and even the required vibration absorbing function cannot be exhibited. For this reason, in order to realize vibration damping, there is a problem in terms of apparatus cost and apparatus dimensions that it is necessary to separately attach an external damper.
　この一方で、１～２Ｈｚ程度の低周波数の、車両の垂直方向の固有振動数付近に気体減衰機能をもつようにチューイングした従来の空気ばねでは、車両がトンネル内へ高速で進入した場合等のように、１０Ｈｚを越える周波数で車両が高周波振動するときは、流路絞り部が目詰まり状態となって空気の流動が不能となるため、垂直方向の入力に対してばね定数が急激に増加して、車両への乗心地等が大きく悪化するという他の問題があった。 On the other hand, with a conventional air spring that is tuned to have a gas damping function in the vicinity of the natural frequency in the vertical direction of the vehicle at a low frequency of about 1 to 2 Hz, such as when the vehicle enters the tunnel at high speed, etc. Thus, when the vehicle vibrates at a frequency exceeding 10 Hz, the flow restrictor becomes clogged and air flow becomes impossible, so the spring constant increases rapidly with respect to the vertical input. As a result, there is another problem that the riding comfort of the vehicle is greatly deteriorated.
　このような問題点に関し、特許文献２には、「基本形態を空気ばねとし、これに互いに連通する第１液室と第２液室を組み合わせることにより、任意方向の振動を吸収でき、かつ支持荷重の大小に関係なくばね定数を小さく抑えることができ、オリフィスの直径や長さを振動数に合わせて設定すれば、低周波領域および高周波領域のいずれに対しても支持荷重に比例した減衰力が得られ」る、エンジンの防振支持用として好適な液体封入式空気ばねが記載されており、これがために、「対向する２枚の基板間に基板と直交する軸線に沿って配置されて２枚の基板を連結する気室と液室とからなり、２枚の基板の一方が他方に対して任意方向に弾性的に変位できるように構成されており、気室が空気ばね機能を備え、液室がオリフィスを有する仕切り板によって基板の一方に接する第１液室と気室に接する第２液室とに振動減衰機能を備えている。」構成を採用することとしている。 Regarding such a problem, Patent Document 2 states that “the basic configuration is an air spring, and the first liquid chamber and the second liquid chamber communicating with each other can be combined to absorb vibration in any direction and support. The spring constant can be kept small regardless of the magnitude of the load, and if the diameter and length of the orifice are set according to the frequency, the damping force proportional to the support load is applied to both the low frequency range and the high frequency range. A liquid-filled air spring suitable as an anti-vibration support for an engine is described, and for this reason, “a pair of two opposing substrates is disposed along an axis perpendicular to the substrate. It is composed of an air chamber and a liquid chamber connecting two substrates, and one of the two substrates is configured to be elastically displaceable in an arbitrary direction with respect to the other, and the air chamber has an air spring function. The liquid chamber has an orifice It is set to be adopted and a vibration damping function and a second fluid chamber in contact with the first liquid chamber and the air chamber in contact with one of the substrates by a partition plate. "Configuration.
　この特許文献２に記載された空気ばねは、たとえば、「エンジンの搭載で生じる静荷重は、上部基板および液室を満たす液を伝達媒体として気室の気体を加圧し、上記の上部基板は気体圧力および受圧面積で定まる所定の高さに支持される。そして、エンジンの駆動により発生する振動の鉛直方向成分は、液室を満たす液の弾性定数が気室の加圧気体に比べて著しく大きいため、液を介して加圧気体に伝えられ、主として加圧気体の弾性変形で吸収され、上記の液はオリフィスを介して液室間を移動する際の摩擦抵抗により、振動を減衰させる。」とするものであって、振動周波数のいかんにかかわらず、液体を、オリフィスを介して二つの液室間に流動させて振動を減衰させるものであることから、振動の減衰のために、空気ばねに外部ダンパーを付設することは不要になる。 The air spring described in Patent Document 2 is, for example, “The static load generated when the engine is mounted pressurizes the gas in the air chamber using the liquid that fills the upper substrate and the liquid chamber as a transmission medium, and the upper substrate is a gas The vertical component of the vibration generated by driving the engine is significantly higher than that of the pressurized gas in the air chamber. Therefore, it is transmitted to the pressurized gas through the liquid and absorbed mainly by the elastic deformation of the pressurized gas, and the liquid attenuates the vibration due to the frictional resistance when moving between the liquid chambers through the orifice. In order to attenuate the vibration, the air spring is used for damping the vibration because the liquid flows between the two liquid chambers through the orifice regardless of the vibration frequency. To outside Be attached the bumpers is not required.
特開２００６－３２９２８０号公報JP 2006-329280 A 特開平１１－１０１２８７号公報Japanese Patent Laid-Open No. 11-101287
　しかるに、特許文献２に記載された液体封入式空気ばねでは、気室と液室との間を隔膜としてダイヤフラムで仕切ることとしており、そのダイヤフラムには常に液室内圧が作用することになって、気室内圧もまた必然的に高くなる他、気室内圧が上に乗る荷重に左右されることになるため、空気ばねを、十分な振動吸収機能を発揮できるようにコントロールすることができないという問題があった。
　しかも、この空気ばねは、気室内の気体の流動に基く、減衰機能を発揮し得ないことから、車両の低周波振動に対し、感度の高いすぐれた気体減衰機能を発揮することもまた不可能であった。 However, in the liquid-filled air spring described in Patent Document 2, the air chamber and the liquid chamber are separated by a diaphragm as a diaphragm, and the pressure in the liquid chamber always acts on the diaphragm. The air chamber pressure also inevitably increases, and because the air chamber pressure depends on the load on top, the air spring cannot be controlled to provide sufficient vibration absorbing function. was there.
In addition, since this air spring cannot exhibit a damping function based on the flow of gas in the air chamber, it is also impossible to exhibit a highly sensitive gas damping function with high sensitivity to low-frequency vibrations of the vehicle. Met.
　この発明は、従来技術が抱えるこのような問題点を解決することを課題とするものであり、その目的とするところは、車両の低周波振動を、すぐれた応答性の下で十分に吸収するとともに減衰させることができ、併せて、空気ばねの流路絞り部が目詰まりを生じるほどの高周波振動に対しては、液体減衰手段の作用下で、振動を減衰させることができる空気ばね装置を提供するにある。 The object of the present invention is to solve such problems of the prior art, and the object of the present invention is to sufficiently absorb the low-frequency vibration of the vehicle with excellent responsiveness. In addition, an air spring device that can dampen the vibration under the action of the liquid attenuating means against high frequency vibration that can be damped together with the flow restriction of the air spring. In offer.
　この発明の空気ばね装置は、上面板および下面板と、これらのそれぞれの面板に、それぞれの端部を気密に連結した筒状可撓膜体とからなり、内部に、大気圧以上の加圧気体を封入してなる空気ばねと、この空気ばねの上面板側もしくは下面板側に配設されて、垂直方向下向きの入力によって主には剪断変形される、ゴムを主体とする剪断ばね手段とを具えるものであって、空気ばねに、垂直方向の入力に対する気体減衰機構を設けるとともに、剪断ばね手段内に、気体減衰機構から独立して垂直方向の入力を減衰させる液体減衰手段を設けてなるものである。 The air spring device of the present invention comprises an upper plate and a lower plate, and a cylindrical flexible film body in which the respective end portions are airtightly connected to the respective face plates, and the inside thereof is pressurized at or above atmospheric pressure. An air spring formed by enclosing gas, and a shear spring means mainly composed of rubber, which is disposed on the upper surface plate side or the lower surface plate side of the air spring and is mainly subjected to shear deformation by a vertically downward input. The air spring is provided with a gas damping mechanism for the vertical input, and the shear spring means is provided with a liquid damping means for damping the vertical input independently of the gas damping mechanism. It will be.
　ここで、気体減衰機構は、上面板もしくは下面板に連結した加圧気体の貯留容器と、上面板もしくは下面板、または、気体貯留容器に到る中間部に設けた流路絞り部とで構成することができる。 Here, the gas attenuating mechanism is composed of a pressurized gas storage container connected to the upper surface plate or the lower surface plate, and a flow path restricting portion provided at the upper surface plate or the lower surface plate, or an intermediate portion reaching the gas storage container. can do.
　また、前記液体減衰手段は、剪断ばね手段に設けた窪みと、この窪みの開口を液体の封入下で閉止する、空気ばねから独立させたダイアフラムとで区画形成される液室の、仕切り部材によって分割されるそれぞれの分割液室を、液室内もしくは液室外に設けた絞り通路によって相互に連結させることにより構成することが好ましい。 The liquid attenuating means is formed by a partition member of a liquid chamber that is partitioned by a recess provided in the shear spring means and a diaphragm independent of the air spring that closes the opening of the recess when the liquid is sealed. It is preferable that the divided liquid chambers to be divided are connected to each other by a throttle passage provided outside the liquid chamber or outside the liquid chamber.
　またここで、空気ばねと剪断ばね手段とは、垂直方向の入力に対して直列に配置することが好ましく、そして、垂直方向下向きの入力によって主には圧縮変形される、ゴムを主体とする圧縮ばね手段をもまた設けることが好ましい。 Here, the air spring and the shear spring means are preferably arranged in series with respect to the input in the vertical direction, and the compression mainly composed of rubber that is mainly compressed and deformed by the input in the vertical direction downward. Preferably spring means are also provided.
　なお、圧縮ばね手段を設けるときは、その圧縮ばね手段と剪断ばね手段とをまた、垂直方向の入力に対して直列に配置することが好ましい。 When the compression spring means is provided, the compression spring means and the shear spring means are preferably arranged in series with respect to the vertical input.
　ところで、剪断ばね手段は、剪断力だけを発生するものとすることも可能であるが、それを、円錐台状もしくは角錐台状の錐台形状ゴム部材と、ゴム部材の変形抑制に寄与する錐台形状剛性板との交互の積層体の、芯体おおび外筒への接合構造体としたときは、垂直方向下向きの入力に対して、圧縮変形等を伴う剪断変形を行わせることで、ゴム部材の耐久性を確保しつつ、発生ばね力の大きさを、それぞれのテーパ角度等の選択の下で簡易に調整することができる。 By the way, the shear spring means can generate only a shearing force, but it is composed of a truncated cone-shaped or truncated pyramidal frustum-shaped rubber member and a cone that contributes to suppressing deformation of the rubber member. When the laminated body of the alternate structure with the trapezoidal rigid plate is a joined structure to the core body and the outer cylinder, by causing a shear deformation accompanied by a compressive deformation or the like to the downward input in the vertical direction, While ensuring the durability of the rubber member, the magnitude of the generated spring force can be easily adjusted under the selection of the respective taper angles.
　さらに、圧縮ばね手段は、円環状のゴム板と、円環状の剛性板との交互の積層体の、下端支持プレートおよび上端リングへの接合構造体とすることが、圧縮方向の所要のばね力の発生を担保するとともに、水平方向の、小さな剪断ばね力の発生を担保する上で好ましい。 Further, the compression spring means may be a structure in which an alternate laminated body of an annular rubber plate and an annular rigid plate is joined to the lower end support plate and the upper end ring, and a required spring force in the compression direction. It is preferable to secure the occurrence of the small shear spring force in the horizontal direction.
　この発明の空気ばね装置では、たとえば鉄道車両の通常走行時の、垂直方向の振動および、１～２Ｈｚ程度の低周波固有振動に対しては、主には、空気ばねおよび剪断ばね手段の弾性変形によって、すぐれた応答性の下で、振動を有効に吸収することができ、また、加圧気体が、気体減衰機構の作用下にて、空気ばねと気体貯容器との間で、流路絞り部を経て流動することによる、いわゆる拡散減衰、流路絞り部が加圧気体に及ぼす摩擦抵抗等に基づくエネルギ吸収その他によって、振動を有効に減衰させることができる。 In the air spring device of the present invention, for example, the elastic deformation of the air spring and the shear spring means mainly against vibrations in the vertical direction and low-frequency natural vibrations of about 1 to 2 Hz during normal running of a railway vehicle. By virtue of this, vibration can be effectively absorbed under excellent responsiveness, and the compressed gas can flow between the air spring and the gas storage container under the action of the gas damping mechanism. The vibration can be effectively damped by so-called diffusion attenuation by flowing through the part, energy absorption based on frictional resistance or the like exerted on the pressurized gas by the flow path restricting part, and the like.
　しかも、この空気ばね装置では、車両がトンネル内等へ高速で進入することその他によって、車両が１０Ｈｚを越える周波数で高周波振動されて、空気ばねの流路絞り部が目詰まり状態となり、加圧空気の、上述したような流動が不能となった場合にあっても、空気ばねから独立させて設けた液体減衰装置は、そのチューニングによって、十分な振動減衰機能を発揮できるので、空気ばね装置全体のばね力を極端に増加させることなく、いいかえれば、車両への乗心地を十分に確保しつつ、液体減衰装置内での液体の流動に基く振動減衰機能を効果的に発揮させることができる。 In addition, in this air spring device, the vehicle is vibrated at a frequency exceeding 10 Hz due to the vehicle entering the tunnel or the like at high speed, and the flow restrictor of the air spring becomes clogged. Even when the flow as described above becomes impossible, the liquid damping device provided independently of the air spring can exhibit a sufficient vibration damping function by tuning, so that the entire air spring device In other words, without excessively increasing the spring force, the vibration damping function based on the flow of the liquid in the liquid damping device can be effectively exhibited while sufficiently securing the riding comfort of the vehicle.
　このように、この空気ばね装置では、気体減衰機構と、液体減衰手段とを相互に独立させて設け、それらのそれぞれを、相互の影響なしに別個に機能させることによって、車両の低周波振動を、高い応答性の下で十分に吸収するとともに減衰させることができ、また、気体減衰機構の流路絞り部が目詰まりを生じるほどの高周波振動に対しては、液体減衰手段の作用で、振動を効果的に減衰させることができる。
　なお、このような振動減衰機能は、空気ばねがパンク等によってデフレートされた場合にもまた同様に発揮させることができる。 Thus, in this air spring device, the gas damping mechanism and the liquid damping means are provided independently of each other, and each of them functions separately without mutual influence, thereby reducing the low frequency vibration of the vehicle. It can absorb and dampen well under high responsiveness, and the high-frequency vibration that clogs the flow restrictor of the gas damping mechanism Can be effectively attenuated.
It should be noted that such a vibration damping function can be similarly exerted even when the air spring is deflated by puncture or the like.
　ここで、気体減衰機構を、上面板もしくは下面板に連結した、加圧気体の貯留容器と、上面板もしくは下面板、または、気体貯留容器に到る中間部に設けた流路絞り部とで構成するときは、振動減衰機能を有する従来の空気ばねに大きな変更を加えることなしに、所要の気体減衰機構を構成することができる。 Here, the gas damping mechanism is connected to the upper surface plate or the lower surface plate, and the pressurized gas storage container, and the upper surface plate or the lower surface plate, or the flow restrictor provided in the intermediate portion leading to the gas storage container. When configured, a required gas damping mechanism can be configured without making a major change to a conventional air spring having a vibration damping function.
　また、液体減衰手段を、剪断ばね手段に設けた窪みと、この窪みの開口を、液体の封入下で閉止するダイヤフラムとで形成される液室の、仕切部材によって二分割されるそれぞれの分割液室を、絞り通路によって相互に連通させて構成する場合は、気体減衰機構から完全に独立した液体減衰手段を極めてコンパクトに構成することができる。このことは、絞り通路を液室内に設けた場合により効果的である。
　この一方で、絞り通路を液室外に設ける場合は、絞り通路長さの選択の自由度を高めて、振動減衰に寄与する所要の液柱共振周波数の実現を容易にすることができ、また、十分長い通路を確保して、摩擦抵抗による振動減衰能力を高めることができる。 Further, each of the divided liquids divided into two by the partition member of the liquid chamber formed by the recess provided in the shear spring means with the liquid attenuating means and the diaphragm for closing the opening of the recess when the liquid is sealed. When the chambers are configured to communicate with each other by a throttle passage, the liquid damping means completely independent from the gas damping mechanism can be configured very compactly. This is more effective when the throttle passage is provided in the liquid chamber.
On the other hand, when the throttle passage is provided outside the liquid chamber, the degree of freedom in selecting the throttle passage length can be increased, and the required liquid column resonance frequency contributing to vibration damping can be easily realized. A sufficiently long path can be secured to increase the vibration damping capability due to frictional resistance.
　ここで、空気ばねと剪断ばね手段とを、垂直方向の入力に対して直列に配置したときは、直列ばねの原理によって、ばね定数の小さい方の性能を顕在化させて、車両の垂直方向振動を、柔軟に弾性支持するとともに、減衰させることができる。 Here, when the air spring and the shear spring means are arranged in series with respect to the input in the vertical direction, the performance of the smaller spring constant is manifested by the principle of the series spring, and the vertical vibration of the vehicle Can be elastically supported and damped.
　またここで、垂直方向下向きの入力によって主には圧縮変形される、ゴムを主体とする圧縮ばね手段を設けたときは、たとえば、空気ばねおよび剪断ばね手段がともに変形限界に達した後に、圧縮ばね手段の硬いばね特性の下で振動を弾性支持することで、車両の走行安定性を確保することができ、このことは、空気ばねがパンク等によってデフレートされて、それ本来の機能を発揮し得なくなった後、剪断ばね手段および圧縮ばね手段の両者によって垂直入力を弾性支持する場合にもほぼ同様である。 Here, when the compression spring means mainly composed of rubber, which is mainly compressed and deformed by the downward input in the vertical direction, is provided, for example, after both the air spring and the shear spring means reach the deformation limit, the compression is performed. By supporting the vibration elastically under the hard spring characteristics of the spring means, it is possible to ensure the running stability of the vehicle. This is because the air spring is deflated by puncture etc. and exhibits its original function. The same applies to the case where the vertical input is elastically supported by both the shear spring means and the compression spring means after it is not obtained.
　なお、このような空気ばね装置に水平方向の力が入力されたときは、主には、空気ばねの水平変形と、圧縮ばね手段の剪断変形とによって、その力を柔軟に弾性支持することができる。
　そして、圧縮ばね手段による水平入力のこのような弾性支持は、空気ばねのデフレートの有無にかかわらず、主には、圧縮ばねの剪断ばね特性の顕在化の下で、垂直荷重の大小のいかんにかかわらず、十分柔軟に行われることになる。 When a horizontal force is input to such an air spring device, the force can be flexibly elastically supported mainly by the horizontal deformation of the air spring and the shear deformation of the compression spring means. it can.
Such elastic support of the horizontal input by the compression spring means is mainly applied to the magnitude of the vertical load under the manifestation of the shear spring characteristics of the compression spring, regardless of the presence or absence of the deflate of the air spring. Regardless, it will be flexible enough.
　従ってこの装置では、剪断ばね手段が、それの変形限界まで変形するほどの大きな垂直方向下向きの入力を受け、それ以後の垂直方向下向きの入力の弾性支持は専ら圧縮ばね手段の作用によって行われることになっても、水平方向の入力に対しては、空気ばねがデフレートされていると否とにかかわらず、圧縮ばね手段の剪断変形をもって柔軟に弾性支持することができる。 Therefore, in this device, the shear spring means receives a vertical downward input large enough to deform to its deformation limit, and the subsequent elastic support of the vertical downward input is performed exclusively by the action of the compression spring means. Even if it becomes, it can be elastically supported flexibly with the shearing deformation of the compression spring means regardless of whether the air spring is deflated or not for the input in the horizontal direction.
　そしてまた、剪断ばね手段を、錐台形状ゴム部材と、錐台形状剛性板との交互の積層体の、内筒とすることができる芯体および外筒への接合構造体としたときは、垂直方向下向きの入力に対し、ゴム部材を、剪断方向に加え、圧縮方向にも変形させて、ばね定数の幾分の増加傾向の下で、剪断変形だけを行わせる場合に比して、ゴム部材の絶対変形量を抑制することができるので、ゴム部材の耐久性を高めることができ、この一方で、剪断ばね手段を、水平方向の入力に対しても弾性機能の発揮に寄与させることができる。 And when the shear spring means is a joined structure to the core body and the outer cylinder, which can be the inner cylinder, of the alternately laminated body of the frustum-shaped rubber member and the frustum-shaped rigid plate, Compared to a case where the rubber member is deformed in the compression direction in addition to the shearing direction in response to the vertical downward input, the rubber member is subjected to only the shear deformation under a tendency of increasing the spring constant. Since the absolute deformation amount of the member can be suppressed, the durability of the rubber member can be increased. On the other hand, the shear spring means can contribute to the exertion of the elastic function even with respect to the horizontal input. it can.
　また、圧縮ばね手段を、たとえば、水平な下端支持プレート上に接合される、ともに水平な、円環状ゴム板と、円環状剛性板との交互の積層体の、これも水平な上端リングへの接合構造体としたときは、そこへの垂直方向下向きの入力の作用時には、圧縮ばね手段に硬いばね特性を発揮させる一方で、水平方向の入力に対しては、円環状ゴム板の剪断変形下で、柔軟なばね特性を発揮させることができる。 Also, the compression spring means may be joined to, for example, a horizontal lower end support plate, which is an alternating laminate of annular rubber plates and annular rigid plates, both horizontally, also to the horizontal upper ring. When the joint structure is used, the compression spring means exerts a hard spring characteristic when the vertical downward input is applied thereto, while the annular rubber plate is subjected to shear deformation for the horizontal input. Thus, flexible spring characteristics can be exhibited.
　なお、剪断ばね手段および圧縮ばね手段のそれぞれを、空気ばね側から順次に配設して、それらを、垂直方向の入力に対して直列配置としたときは、たとえば、垂直方向下向きの入力の弾性支持を、剪断ばね手段から圧縮ばね手段に肩代わりさせてなお、下端支持プレートと剪断ばね手段との間に隙間を確保することで、簡単な構造の装置をもって、上記の各種機能を十分に発揮させることができ、しかも、剪断ばね手段が、垂直方向下向き入力によって限界位置まで変形されていても、圧縮ばね手段を、水平方向の入力の弾性支持のために、十分円滑に、かつ確実に機能させることができる。 In addition, when each of the shear spring means and the compression spring means is sequentially arranged from the air spring side and they are arranged in series with respect to the vertical input, for example, the elasticity of the vertically downward input By supporting the support from the shearing spring means to the compression spring means, and ensuring a gap between the lower end support plate and the shearing spring means, the above-mentioned various functions can be sufficiently exerted with a device having a simple structure. In addition, even if the shear spring means is deformed to the limit position by the vertical downward input, the compression spring means functions sufficiently smoothly and reliably for the elastic support of the horizontal input. be able to.
　ところで、剪断ばね手段の、内筒とすることができる芯体を、たとえば、圧縮ばね手段の上端リングに取付けたときは、圧縮ばね手段の中空部寸法との関連の下で、その中空部内へ、剪断ばね手段の一部を進入させて配置することが可能となり、これにより、装置の占有空間、ひいては、外形寸法の小型化を図ることができ、鉄道車両の低床化を実現することができる。 By the way, when the core body of the shearing spring means, which can be the inner cylinder, is attached to the upper end ring of the compression spring means, for example, into the hollow part in relation to the dimension of the hollow part of the compression spring means. It is possible to arrange a part of the shearing spring means so that the space occupied by the apparatus, and thus the outer dimensions can be reduced, and the floor of the railway vehicle can be reduced. it can.
この発明の実施形態を示す縦断面図である。It is a longitudinal cross-sectional view which shows embodiment of this invention.
　図１は、この発明の実施の形態を示す縦断面図であり、図中１は、たとえば水平姿勢で車体側に取付けられる上面板を、また２は下面板を、そして３は、それらの両面板１，２にそれぞれの端部を気密に連結した、図ではセルフシール構造の筒状可撓膜体をそれぞれ示し、これらの部材１，２，３は、内部に、空気、不活性ガス等とすることができる所定の圧力の気体を封入することで空気ばね４を構成する。
　ここではまた、この空気ばね４の上面板１に、流路絞り部としてのボス５を設け、このボス５を介して空気ばね４を、図示しない、加圧気体の貯留容器に連通させることで、その貯留容器とボス５とで、垂直方向の入力に対する気体減衰機構を構成する。
　なお、この気体減衰機構は、鉄道車両等への乗心地の確保を第一義として、１～２Ｈｚ程度の低周波振動を減衰するべく、ボス５の寸法等をチューニングされている。 FIG. 1 is a longitudinal sectional view showing an embodiment of the present invention. In the figure, 1 is an upper surface plate attached to the vehicle body side, for example, in a horizontal posture, 2 is a lower surface plate, and 3 is both surfaces thereof. The ends of the plates 1 and 2 are hermetically connected to each other. In the figure, the cylindrical flexible film bodies having a self-sealing structure are shown. These members 1, 2 and 3 are internally provided with air, inert gas, etc. The air spring 4 is configured by enclosing a gas having a predetermined pressure.
Here, a boss 5 as a flow passage restricting portion is provided on the upper surface plate 1 of the air spring 4, and the air spring 4 is communicated with a pressurized gas storage container (not shown) via the boss 5. The storage container and the boss 5 constitute a gas damping mechanism for vertical input.
In this gas damping mechanism, the dimensions of the boss 5 and the like are tuned so as to attenuate low frequency vibrations of about 1 to 2 Hz, with the primary aim of ensuring riding comfort on a railway vehicle or the like.
　そして、このような空気ばね４の下面板２側に、剪断ばね手段６および圧縮ばね手段７のそれぞれを直列に配設して、空気ばね４と、剪断ばね手段６と、圧縮ばね手段７とを順次の直列整列構造とする。
　このことによれば、垂直方向の入力に対して、ばね定数の低い方の性能が顕在化する柔らかいばね特定がもたらされる。
　なお、剪断ばね手段６と、圧縮ばね手段７とは、図に示すところとは順序を入れ換えて配設することも可能である。 The shear spring means 6 and the compression spring means 7 are arranged in series on the lower surface plate 2 side of the air spring 4, and the air spring 4, the shear spring means 6, the compression spring means 7, and the like. Are sequentially arranged in series.
This results in a soft spring identification that reveals the performance of the lower spring constant for vertical input.
Note that the shear spring means 6 and the compression spring means 7 can be arranged in a different order from that shown in the figure.
　またこの図に示すところでは、垂直方向の下向き入力によって主には剪断変形される、ゴムを主体とする剪断ばね手段６を、図の下方側に向けて寸法が次第に大きくなる円錐台状、角錐台状等の錐台形状をなすゴム部材６ａと、同様の錐台形状剛性板６ｂとの交互の積層体の、図では軽量化のためにほぼ筒状とした、外表面が同様の錐台形状の芯体８ａおよび、外筒８ｂへの接合構造体とする。 Further, in the figure, the shear spring means 6 mainly composed of rubber, which is mainly shear-deformed by a downward input in the vertical direction, has a truncated cone shape and a pyramid whose dimensions gradually increase toward the lower side of the figure. A frustum with an outer surface having a substantially cylindrical shape for weight reduction in an alternating laminate of a rubber member 6a having a frustum shape such as a trapezoid and a similar frustum-shaped rigid plate 6b. It is set as the joining structure body to the shape core body 8a and the outer cylinder 8b.
　そしてまた、垂直方向の下向き入力によって主には圧縮変形される、ゴムを主体とする圧縮ばね手段７を、下面板２の下方側に離隔して位置して、たとえば水平姿勢で台車に取付けられる下端支持プレート９ａに接合される、円環状の水平なゴム板７ａと、円環状の同様の剛性板７ｂとの交互の積層体の、その下端支持プレート９ａおよび上端リング９ｂへの接合構造体としてなり、ゴム板７ａ，剛性板７ｂおよび上端リング９ｂのそれぞれの内径を均一径としてなる。 Further, the compression spring means 7 mainly composed of rubber, which is mainly compressed and deformed by the downward input in the vertical direction, is located on the lower side of the lower surface plate 2 and is attached to the carriage in a horizontal posture, for example. As a joining structure of the alternate laminated body of the annular horizontal rubber plate 7a and the annular rigid plate 7b joined to the lower end support plate 9a to the lower end support plate 9a and the upper end ring 9b. Thus, the inner diameters of the rubber plate 7a, the rigid plate 7b, and the upper end ring 9b are made uniform.
　空気ばね４の下面板２の下方側に、図示のように配設されるそれぞれのばね手段６、７は、ここでは、剪断ばね手段６の外筒８ｂを下面板２の下面側に取付ける一方で、それの芯体８ａの下端部分を、圧縮ばね手段７の上端リング９ｂに掛合させたフランジ部材１０を介して、圧縮ばね手段７の中空部７ｃ内へ入れ込んで、その芯体８ａの下端を、圧縮ばね手段７が圧縮変形されてなお、下端支持プレート９ａに当接しない程度に下端支持プレート９ａから離隔して位置するように相互に組付けることで、空気ばね４に取り付けることができる。
　このように剪断ばね手段６の芯材８ａを、圧縮ばね手段７の中空部７ｃ内へ入れ込んで配置することで、装置全体の小型化を図ることができる。 Each of the spring means 6, 7 arranged as shown in the figure below the lower surface plate 2 of the air spring 4 is here one for attaching the outer cylinder 8 b of the shear spring means 6 to the lower surface side of the lower surface plate 2. Then, the lower end portion of the core body 8a is inserted into the hollow portion 7c of the compression spring means 7 via the flange member 10 engaged with the upper end ring 9b of the compression spring means 7, and the core body 8a It is possible to attach the lower end to the air spring 4 by assembling the lower ends so as to be positioned away from the lower end support plate 9a so as not to contact the lower end support plate 9a even after the compression spring means 7 is compressed and deformed. it can.
In this way, the core material 8a of the shear spring means 6 is placed in the hollow portion 7c of the compression spring means 7 so that the entire apparatus can be reduced in size.
　なおこの図に示すところでは、剪断ばね手段６の、最も内周側に位置するゴム部材６ａの、垂直方向の下向き入力による剪断変形等による変形は、最も内周側に位置する錐台形状剛性板６ｂがフランジ部材１０に当接することによって阻止されることになり、剪断ばね手段６のこれ以上の剪断変形、ひいては、下面板２の、その後に続く下降変位は、後に述べる液体減衰手段の作用の下にて行われることになる。 In this figure, the deformation of the rubber member 6a located on the innermost circumferential side of the shearing spring means 6 due to shear deformation or the like caused by the downward downward input in the vertical direction is the frustum-shaped rigidity located on the innermost circumferential side. The plate 6b is prevented from coming into contact with the flange member 10, and further shear deformation of the shear spring means 6, and further subsequent downward displacement of the lower face plate 2, causes the action of the liquid damping means described later. Will be performed under.
　なお、図中１ａ、２ａはそれぞれ、上面板１の下面、および下面板２の上面のそれぞれに設けた摺接板を示し、たとえば、それぞれステンレス板および、ポリテトラフロオロエチレン板とすることができるこれらの摺接板１ａ、２ａは、垂直方向の大きな荷重の作用または、空気ばね４のデフレート等に起因して、両面板１、２が当接した場合に、それらの面板１、２の水平面内での摺動変位を十分円滑なものとするべく機能する。 In the figure, reference numerals 1a and 2a denote sliding plates provided on the lower surface of the upper surface plate 1 and the upper surface of the lower surface plate 2, respectively, for example, a stainless steel plate and a polytetrafluoroethylene plate, respectively. These slidable contact plates 1a and 2a are formed when the double-sided plates 1 and 2 come into contact with each other due to the action of a large vertical load or the deflation of the air spring 4 or the like. It functions to make the sliding displacement in a horizontal plane sufficiently smooth.
　ところでこの発明では、上述したところに加え、剪断ばね手段６に、前述した気体減衰機構からは完全に独立して、垂直方向の入力の減衰をもたらす液体減衰手段１１を設ける。
　図示のこの液体減衰手段１１は、剪断ばね手段６の頂部に形成した窪み１２と、この窪み１２の開口を、液体の封入下で閉止するダイヤフラム１３とで形成される液室１４の、剛性仕切部材１５によって二分割されるそれぞれの分割液室１４ａ、１４ｂを、たとえば液室１４内に設けた絞り通路１６によって相互に連通させることによって構成してなり、ここで、ダイアフラム１３の外表面側は大気に開放してなる。 By the way, in the present invention, in addition to the above, the shear spring means 6 is provided with the liquid attenuating means 11 that causes the attenuation of the input in the vertical direction completely independently of the gas attenuating mechanism.
The liquid damping means 11 shown in the figure is a rigid partition of a liquid chamber 14 formed by a recess 12 formed at the top of the shearing spring means 6 and a diaphragm 13 that closes the opening of the recess 12 under liquid filling. Each of the divided liquid chambers 14a and 14b divided by the member 15 is configured to communicate with each other by, for example, a throttle passage 16 provided in the liquid chamber 14, where the outer surface side of the diaphragm 13 is Open to the atmosphere.
　かかる液体減衰手段１１は、空気ばね側の気体減衰機構が、たとえば、流路絞り部としてのボス５の目詰まり現象等によって振動減衰機能を発揮し得なくなり、この結果として、空気ばね４のばね定数の増加が余儀なくされた場合や、空気ばね４がパンク等によってデフレートされた場合等において、剪断ばね手段６の、垂直方向の下方に向く変形に伴って、たとえば、下側の分割液室１４ａの液室内圧が増加すると、その液室１４ａ内の液体が、絞り通路１６を経て上側の分割液室１４ｂに流入することにより、両液室１４ａ、１４ｂの内圧が平衡状態とされ、逆に、その下側分割液室１４ａの液室内圧が低減されると、上側分割液室１４ｂ内の液体が、絞り通路１６を経て下側分割液室１４ａ内に流入して、両液室内圧の平衡化がもたらされる。
　そして、これらのいずれの場合にあっても、液体が絞り通路１６内を流動するに当っての液柱共振、摩擦抵抗等によって、振動の効果的な減衰をもたらすことができる。 In the liquid damping means 11, the gas damping mechanism on the air spring side cannot exhibit the vibration damping function due to, for example, the clogging phenomenon of the boss 5 as the flow path restricting portion. As a result, the spring of the air spring 4 When the constant is forced to increase or when the air spring 4 is deflated by puncture or the like, the shear spring means 6 is deformed downward in the vertical direction. When the liquid chamber pressure increases, the liquid in the liquid chamber 14a flows into the upper divided liquid chamber 14b through the throttle passage 16, so that the internal pressures of both the liquid chambers 14a and 14b are brought into an equilibrium state. When the liquid chamber pressure in the lower divided liquid chamber 14a is reduced, the liquid in the upper divided liquid chamber 14b flows into the lower divided liquid chamber 14a via the throttle passage 16, and the pressure in both liquid chambers is reduced. Equilibration comes It is.
In any of these cases, the vibration can be effectively damped by liquid column resonance, frictional resistance, and the like when the liquid flows in the throttle passage 16.
　すなわち、液体減衰手段１１は、ある一定領域の高周波振動に対して有効に機能するようにチューイングされており、その領域の振動より低周波の振動は通常、空気ばね４の流路絞り部による減衰機構によって十分に減衰されることになる。 That is, the liquid damping means 11 is tuned so as to function effectively with respect to high-frequency vibrations in a certain region, and vibrations having a lower frequency than the vibrations in that region are normally attenuated by the flow restrictor of the air spring 4. It will be sufficiently damped by the mechanism.
　以上に述べたように、空気ばね４と、剪断ばね手段６と圧縮ばね手段７とを、垂直方向の入力に対して直列配置となるよう構成して、気体減衰機構および、この気体減衰機構から独立させた液体減衰機構１１を設けてなるこの空気ばね装置は、それを、たとえば、鉄道車両用のボルスタレス台車に適用した場合には、各種の寸法の、所要に応じた選択の下で、一般的に要求される、上下および左右方向の、およそ±４０ｍｍ程度までの振動に十分に対処することができ、また、前後方向の１５０ｍｍ程度の大変位も十分に吸収することができる。
　この場合、上下、左右方向の振動は、空気ばね４によって、また、前後方向の変位は、空気ばね４と、圧縮ばね手段７によって吸収されることになる。 As described above, the air spring 4, the shear spring means 6, and the compression spring means 7 are configured to be arranged in series with respect to the input in the vertical direction, and the gas damping mechanism and the gas damping mechanism are When this air spring device provided with the independent liquid damping mechanism 11 is applied to, for example, a bolsterless bogie for a railway vehicle, it is generally used under various selections according to requirements. Therefore, it is possible to sufficiently cope with vibrations up to about ± 40 mm in the vertical and horizontal directions, and to sufficiently absorb a large displacement of about 150 mm in the front-rear direction.
In this case, vibrations in the vertical and horizontal directions are absorbed by the air spring 4, and displacement in the front and rear direction is absorbed by the air spring 4 and the compression spring means 7.
　そしてまた、空気ばね４が、パンク等した後は、上面板１等の、剪断ばね手段６上への着座に基づき、上下方向の振動はその剪断ばね手段６により、そして、左右方向の振動は、圧縮ばね手段７によりそれぞれ吸収されることになり、さらに、前後方向の大変位は、摺接板１ａ、２ａの作用に基く滑り変位によって吸収されることになる。 Further, after the air spring 4 is punctured, the vertical vibration is caused by the shear spring means 6 based on the seating of the top plate 1 etc. on the shear spring means 6, and the horizontal vibration is The large displacement in the front-rear direction is absorbed by the sliding displacement based on the action of the sliding contact plates 1a, 2a.
　さらに、垂直方向の低周波振動は、振動乗心地の確保のために、１～２Ｈｚ程度の低周波振動数にチューイングされた前記気体減衰機構による、ボス５を通る加圧気体の流動によって減衰されることになる。
　これにより、装置が、たとえば１０～２０Ｈｚ程度の高周波振動を受けて、気体減衰機構が所期した減衰機能を発揮し得なくなって、空気ばね４のばね定数が増加する場合等には、剪断ばね手段６の剪断変形に伴う液体減衰手段１１の作用の下で振動が減衰されることになるので、車両等への快適な乗り心地を確保することができる。 Further, the low frequency vibration in the vertical direction is damped by the flow of pressurized gas through the boss 5 by the gas damping mechanism that is tuned to a low frequency frequency of about 1 to 2 Hz in order to ensure vibration riding comfort. Will be.
As a result, when the apparatus receives high frequency vibration of about 10 to 20 Hz, for example, and the gas damping mechanism cannot perform the intended damping function, and the spring constant of the air spring 4 increases, the shear spring is used. Since the vibration is attenuated under the action of the liquid attenuating means 11 accompanying the shear deformation of the means 6, it is possible to ensure a comfortable ride on the vehicle or the like.
　なお、液体減衰手段１１のこのような振動減音機能は、空気ばね４がパンク等によってデフレートされた場合にも発揮させることができるので、空気ばね４が作動不能に到ってなお、液体減衰手段１１をもって、防振および減衰有能を有効に発揮させることができる。 Since the vibration damping function of the liquid damping means 11 can be exhibited even when the air spring 4 is deflated by puncture or the like, the liquid damping is performed even when the air spring 4 becomes inoperable. With the means 11, it is possible to effectively exhibit the vibration proof and damping ability.
１：上面板
１ａ，２ａ：摺接板
２：下面板
３：筒状可撓膜体
４：空気ばね
５：ボス
６：剪断ばね手段
６ａ：ゴム部材
６ｂ：錐台形状剛性板
７：圧縮ばね手段
７ａ：ゴム板
７ｂ：剛性板
８ａ：芯体
８ｂ：外筒
９ａ：下端支持プレート
９ｂ：上端リング
１０：フランジ部材
１１：液体減衰手段
１２：窪み
１３：ダイアフラム
１４：液室
１４ａ，１４ｂ：分割液室
１５：剛性仕切板
１６：絞り通路 1: top plate 1a, 2a: sliding plate 2: bottom plate 3: cylindrical flexible film body 4: air spring 5: boss 6: shear spring means 6a: rubber member 6b: frustum-shaped rigid plate 7: compression spring Means 7a: Rubber plate 7b: Rigid plate 8a: Core body 8b: Outer cylinder 9a: Lower end support plate 9b: Upper end ring 10: Flange member 11: Liquid damping means 12: Depression 13: Diaphragm 14: Liquid chambers 14a, 14b: Division Liquid chamber 15: Rigid partition plate 16: Restriction passage

Claims (8)

  1. 　上面板および下面板と、これらのそれぞれの面板に、それぞれの端部を気密に連結した筒状可撓膜体とからなり、内部に、大気圧以上の圧力の加圧気体を封入してなる空気ばねと、この空気ばねの上面板側もしくは下面板側に配設されて、垂直方向の入力によって主には剪断変形される、ゴムを主体とする剪断ばね手段とを具える空気ばね装置であって、空気ばねに、垂直方向の入力に対する気体減衰機構を設けるとともに、剪断ばね手段内に、気体減衰機構から独立して垂直方向を減衰させる液体減衰手段を設けてなる空気ばね装置。 It consists of an upper surface plate and a lower surface plate, and a cylindrical flexible film body in which the respective end portions are airtightly connected to each of these face plates, and a pressurized gas having a pressure higher than atmospheric pressure is sealed inside. An air spring device comprising an air spring and a shear spring means mainly composed of rubber, which is disposed on the upper surface plate side or the lower surface plate side of the air spring and is mainly subjected to shear deformation by a vertical input. An air spring device comprising a gas damping mechanism for a vertical input in the air spring and a liquid damping means for damping the vertical direction independently of the gas damping mechanism in the shear spring means.
  2. 　気体減衰機構を、上面板もしくは下面板に連結した気体貯留器と、上面板もしくは下面板、または、気体貯留容器に到る中間部に設けた流路絞り部とで構成してなる請求項１に記載の空気ばね装置。 2. The gas attenuation mechanism is constituted by a gas reservoir connected to an upper surface plate or a lower surface plate, and a flow path restricting portion provided at an upper surface plate or a lower surface plate or an intermediate portion reaching the gas storage container. An air spring device according to claim 1.
  3. 　液体減衰手段を、剪断ばね手段に設けた窪みと、この窪みの開口を、液体の封入下で閉止するダイアフラムとで形成される液室の、仕切部材によって二分割されるそれぞれの分割液室を、液室内もしくは液室外に設けた絞り通路によって相互に連通させることにより構成してなる請求項１もしくは２に記載の空気ばね装置。 Each of the divided liquid chambers divided into two by the partition member is formed by a liquid chamber formed by a recess provided with the liquid damping means in the shearing spring means and a diaphragm that closes the opening of the recess when the liquid is sealed. The air spring device according to claim 1, wherein the air spring device is configured to be communicated with each other by a throttle passage provided outside or outside the liquid chamber.
  4. 　空気ばねと剪断ばね手段とを、垂直方向の入力に対して直列に配置してなる請求項１～３のいずれかに記載の空気ばね装置。 The air spring device according to any one of claims 1 to 3, wherein the air spring and the shear spring means are arranged in series with respect to the input in the vertical direction.
  5. 　垂直方向の入力によって主には圧縮変形される、ゴムを主体とする圧縮ばね手段を設けてなる請求項１～４のいずれかに記載の空気ばね装置。 The air spring device according to any one of claims 1 to 4, further comprising compression spring means mainly composed of rubber that is mainly compressed and deformed by an input in a vertical direction.
  6. 　圧縮ばね手段と剪断ばね手段とを、垂直方向の入力に対して直列に配置してなる請求項５に記載の空気ばね装置。 6. The air spring device according to claim 5, wherein the compression spring means and the shear spring means are arranged in series with respect to the vertical input.
  7. 　剪断ばね手段を、円錐台状もしくは角錐台状の錐台形状ゴム部材と、錐台形状剛性板との交互の積層体の、芯材および外筒への接合構造体としてなる請求項１～６のいずれかに記載の空気ばね装置。 The shear spring means is a structure in which an alternating laminated body of a truncated cone-shaped or truncated pyramid-shaped rubber member and a truncated cone-shaped rigid plate is joined to a core member and an outer cylinder. The air spring device according to any one of the above.
  8. 　圧縮ばね手段を、円環状のゴム板と、円環状の剛性板との交互の積層体の、下端支持プレートおよび上端リングへの接合構造体としてなる請求項５もしくは６に記載の空気ばね装置。 7. The air spring device according to claim 5 or 6, wherein the compression spring means is formed as a joint structure to the lower end support plate and the upper end ring of an alternating laminate of an annular rubber plate and an annular rigid plate.
PCT/JP2009/062361 2008-07-24 2009-07-07 Air spring device WO2010010810A1 (en)

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JP2008191300A JP2010025326A (en) 2008-07-24 2008-07-24 Pneumatic spring device
JP2008-191300 2008-07-24

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CN107764566A (en) * 2017-11-05 2018-03-06 西华大学 A kind of auto parts and components mould measurement support system
AT517288A3 (en) * 2015-03-17 2019-08-15 Toyo Tire & Rubber Co air spring
AT517289A3 (en) * 2015-03-17 2019-08-15 Toyo Tire & Rubber Co air spring
WO2020140475A1 (en) * 2019-01-02 2020-07-09 中车株洲电力机车有限公司 Train suspension device and suspended monorail train
CN114382823A (en) * 2022-01-19 2022-04-22 青岛博锐智远减振科技有限公司 Auxiliary spring and air spring of railway vehicle
CN116441743A (en) * 2023-03-31 2023-07-18 惠州市利宏亚五金制品有限公司 Cutting machine for hardware laser cutting

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US8875681B2 (en) * 2011-10-28 2014-11-04 Robert Bosch Gmbh Fuel rail mounting arrangement

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Cited By (6)

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Publication number Priority date Publication date Assignee Title
AT517288A3 (en) * 2015-03-17 2019-08-15 Toyo Tire & Rubber Co air spring
AT517289A3 (en) * 2015-03-17 2019-08-15 Toyo Tire & Rubber Co air spring
CN107764566A (en) * 2017-11-05 2018-03-06 西华大学 A kind of auto parts and components mould measurement support system
WO2020140475A1 (en) * 2019-01-02 2020-07-09 中车株洲电力机车有限公司 Train suspension device and suspended monorail train
CN114382823A (en) * 2022-01-19 2022-04-22 青岛博锐智远减振科技有限公司 Auxiliary spring and air spring of railway vehicle
CN116441743A (en) * 2023-03-31 2023-07-18 惠州市利宏亚五金制品有限公司 Cutting machine for hardware laser cutting

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