JP2009228772A - Damping element and damping device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a damping element and a damping device capable of providing a high damping effect, and capable of securing a desired stroke. <P>SOLUTION: This damping element 1a has a first elastic member 2 and a second elastic member 3 for externally wrapping a predetermined shaft C and mutually separately positioned in the predetermined shaft C direction, a sandwiching object member 4 fluid-tightly sandwiched in the predetermined shaft C direction between the first elastic member 2 and the second elastic member 3, a first member 5 fluid-tightly joined to the opposite side of the sandwiching object member 4 of the first elastic member 2, and a second member 5 fluid-tightly joined to the opposite side of the sandwiching object member 4 of the second elastic member 3, and is characterized in that the sandwiching object member 4 has a throttling means 4b for communicating a first fluid chamber A defined by the first member 5, the first elastic member 2 and the sandwiching object member 4 and filled with fluid, with a second fluid chamber B defined by the sandwiching object member 4, the second elastic member 3 and the second member 5 and filled with the fluid, by applying resistance to the fluid. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a damping element and a damping device that are suitable for use in vehicles such as passenger cars, trucks, and buses.

  In general, in a vehicle, an impact acting on a wheel from the road surface is not directly transmitted to the vehicle body. Therefore, a spring as a shock absorber for reducing the impact is provided between the knuckle and the vehicle body that rotatably supports the wheel. A shock absorber is also interposed between the knuckle and the vehicle body as a damping device that quickly attenuates the energy that the knuckle continuously vibrates with the spring after impact is applied to the knuckle. These constitute a suspension device.

  As the former spring, a coil spring spirally wound with a cylindrical steel material, a torsion bar spring using the torsional rigidity of a rod-shaped steel material, or an air spring using a diaphragm enclosing air or other gas is used. It is done. As the latter shock absorber, an outer cylinder and an inner cylinder are provided so as to overlap in the axial direction, a shaft fixed to the outer cylinder and inserted through the inner cylinder, and an inner cylinder provided on the opposite side of the shaft from the outer cylinder. A cylinder in sliding contact with the inner peripheral surface of the cylinder, filling a liquid chamber such as hydraulic pressure in a liquid chamber above and below the cylinder inside the inner cylinder, and appropriately providing a throttle and a valve in the cylinder, thereby allowing the outer cylinder and the inner cylinder to When the liquid is displaced in the axial direction, a telescopic type that utilizes a damping effect that occurs when the liquid moves between the upper and lower liquid chambers and the liquid passes through the throttle is generally used.

Such a telescopic shock absorber is described in, for example, Patent Document 1 because foreign matter enters from the gap between the outer cylinder and the inner cylinder and the sliding resistance between the shaft and the inner cylinder increases. As described above, it has been proposed to obtain a damping effect by laminating an elastic body such as an elastomer.
Noto 3007530 gazette

  However, in such a conventional technique, since the damping effect is obtained using an elastic body, the damping effect is low as compared with the telescopic type using the damping effect when passing through the liquid restrictor. In addition, there is a problem that it is difficult to secure a stroke necessary for absorbing the relative displacement between the vehicle body and the knuckle, particularly in the vertical direction.

  In view of the above problems, an object of the present invention is to provide an attenuation element and an attenuation device capable of obtaining a high attenuation effect and ensuring a desired stroke.

In order to solve the above problems, the damping element of the present invention is:
A first elastic member and a second elastic member that are encased in a predetermined axis and are spaced apart from each other in a predetermined axial direction, and liquid-tight between the first elastic member and the second elastic member in the predetermined axial direction. A sandwiched member sandwiched between the first elastic member, a first member that is liquid-tightly joined to the opposite side of the sandwiched member of the first elastic member, and a liquid-tight member of the second elastic member opposite to the sandwiched member And a first fluid chamber in which the sandwiched member is defined by the first member, the first elastic member, and the sandwiched member, and is filled with fluid. It comprises a throttle means for providing resistance to the fluid and communicating with the second fluid chamber defined by the sandwiched member, the second elastic member, and the second member and filled with fluid. And

Here, in the damping element,
The predetermined axis may include a vertical direction, and the first elastic member may be positioned above the second elastic member.

Furthermore, in the damping element,
In the predetermined axial direction, it is preferable that the rigidity of the first elastic member is larger than the rigidity of the second elastic member.

  According to this, when an external force is applied in the predetermined axial direction of the damping element, the deformation of the first elastic member in the predetermined axial direction can be made smaller than the deformation of the second elastic member. .

  As a result, when the external force is applied, the amount of change in the volume of the first fluid chamber is made smaller than the amount of change in the volume of the second fluid chamber, and the second fluid chamber is transferred to the first fluid chamber. The fluid can be moved. That is, since resistance is given when the fluid passes through the throttle means, the damping element can obtain a damping effect that attenuates vibration based on the resistance of the fluid.

  Similarly, when the external force no longer acts, there is no difference between the amount of change in the volume of the first fluid chamber and the amount of change in the volume of the second fluid chamber. Since the fluid returns to the fluid chamber, a resistance is given when the fluid passes through the throttling means. Therefore, the damping element can obtain a damping effect that attenuates vibration based on the resistance of the fluid. it can.

  Further, the first elastic member and the second member are configured so as to enclose the predetermined shaft, as compared to the damping element including only the elastic member that does not include the first fluid chamber and the second fluid chamber. In the elastic member, since the area in the cross section perpendicular to the predetermined axis can be reduced and the rigidity in the predetermined axis direction can be reduced, the stroke as the damping element can be made larger.

Here, in the damping element,
A first restricting means for restricting a displacement between the first member and the sandwiched member in a radial direction of the predetermined shaft upon the approaching / separating displacement of the first member and the sandwiched member in the predetermined axis direction; A second restricting means for restricting a displacement between the second member and the sandwiched member in a radial direction of the predetermined shaft when the second member and the sandwiched member are moved toward and away from each other in the predetermined axis direction; preferable.

  According to this, in the radial direction of the predetermined axis, the relative displacement between the first member and the sandwiched member and the relative displacement between the second member and the sandwiched member are suppressed, and the first elasticity It is possible to prevent an excessive force from acting on the member and the second elastic member in the radial direction, and to stabilize the stroke direction when a force is applied to the damping element in the predetermined axial direction.

In order to solve the above-mentioned problem, the attenuation device of the present invention is
The damping element according to claim 4 or 5 is formed by stacking two or more in the predetermined axial direction.

  According to this, by providing two or more layers of the attenuation element, the attenuation effect provided by the attenuation element can be further increased. Along with this, the effect of making the stroke as the damping device larger than that in which the damping element is constituted only by an elastic member that does not include the first fluid chamber and the second fluid chamber. Can be increased.

Furthermore, in the attenuation device,
The second member of the upper damping element and the first member of the lower damping element adjacent to each other in the predetermined axial direction may be made common.

  According to this, since the component of one said attenuation element adjacent to the said predetermined axis direction and the component of the other said attenuation element can be shared in part, the number of parts as said attenuation device can be reduced. Can be reduced.

  ADVANTAGE OF THE INVENTION According to this invention, the damping element and damping device which can ensure a desired stroke while obtaining a high damping effect can be provided.

  The best mode for carrying out the present invention will be described below with reference to the accompanying drawings.

  FIG. 1 is a schematic view showing an embodiment of a suspension device to which a damping device according to the present invention is applied. FIG. 2 is a schematic diagram showing an embodiment of an attenuation device according to the present invention.

  As shown in FIG. 1, a suspension device 51 to which the damping device of the first embodiment is applied includes a knuckle 52, a shock absorber 1, a spring 53, a lower arm 54, a tire 55, a wheel 56, and a ball joint. 57, a lower spring seat 58, an upper spring seat 59, and a rod 60. In FIG. 1, FR indicates the front in the vehicle front-rear direction, IN indicates the inner side in the vehicle width direction, and UP indicates the upper side.

  The knuckle 52 rotatably supports the tire 55 and the wheel 56, and the lower end portion thereof is connected to the outer end portion in the vehicle width direction of the A arm-shaped lower arm 54 via the ball joint 57 and the upper end thereof. The part is connected to the lower end of the shock absorber 1.

  The shock absorber 1 is connected at its upper end to a suspension tower (not shown) on the vehicle body side via a bush and rod 60 (not shown), and its lower end is connected to the upper end of the knuckle 52. The knuckle 52 is prevented from continuing to vibrate due to the vibration from the road surface transmitted via the damping force, and the knuckle 52 is connected to the vehicle body side and corresponds to a damping device.

  The spring 53 includes a lower spring seat 58 provided in a disc shape near the upper end portion of the outer peripheral surface of the shock absorber 1, and an upper spring seat 59 provided in a disc shape on the vehicle body side near the upper end portion of the rod 60. And is formed so as to swirl around the rod 60 to reduce and mitigate vibration transmitted from the tire 55 and the wheel 56 to the vehicle body via the knuckle 52.

  The lower arm 54 includes a so-called A arm that extends in the vehicle width direction and is formed so that the inner side in the vehicle width branches into a bifurcated shape. The outer end in the vehicle width direction, that is, the apex side of the A arm The knuckle 52 is connected to the lower end portion of the knuckle 52 via a ball joint 57, and two locations on the inner side in the vehicle width direction, that is, on the opposite side of the apex of the A arm, are connected to a suspension member (not shown) on the vehicle body side via a bush (not shown). The knuckle 52 and the vehicle body are coupled so as to be swingable.

  In the suspension device 51 configured as described above, when an external force in the vertical direction acts on the tire 55 from the road surface, the knuckle 52 and the lower arm 54 bounce and rebound in the vertical direction using the bush on the vehicle body as a spring, and accordingly the knuckle 52 The distance between the connecting point with the lower end of the shock absorber 1 and the rod 60 expands and contracts in the direction of the central axis of the shock absorber 1.

  In other words, the predetermined axis C coincides with the central axis of the shock absorber 1, and as the knuckle 52 bounces, the upper side inclines in the vehicle width direction with respect to the vertical direction when viewed in the vehicle longitudinal direction, and the lower side rises and falls with rebound. It has the property of tilting inward in the vehicle width direction relative to the direction.

  As shown in FIG. 2, the shock absorber 1 includes two damper cells 1a each including a rubber ring 2, a rubber ring 3, a resistance plate 4, and two seal plates 5 in a predetermined axis C direction. It is configured by stacking as described above. That is, the damper cell 1a constitutes a damping element, and the shock absorber 1 constitutes a damping device. Hereinafter, the form of the damper cell 1a will be described in more detail with reference to FIG. FIG. 3 is a schematic perspective view showing the damping element according to the present invention disassembled and viewed obliquely from above. In FIG. 3, UP indicates the upper side.

  As shown in FIG. 3, the rubber ring 2 is made of rubber that extends in the circumferential direction around a predetermined axis C, and forms a circular column that encloses the predetermined axis C to form a first elastic member. Similarly, the rubber ring 3 is made of rubber that extends in the circumferential direction about the predetermined axis C, and forms a circular column that encloses the predetermined axis C to form a second elastic member.

  The resistance plate 4 does not allow any of the hydraulic oil and nitrogen gas that make up the fluid to permeate. For example, the resistance plate 4 has a non-permeating portion 4a formed in an annular shape with a molten material or synthetic resin such as iron or aluminum, It has fine pores that allow any of the constituting hydraulic oil and nitrogen gas to pass therethrough, reduce the flow velocity when the fluid passes and impart resistance to the fluid, for example, sintered material, hollow fat membrane, porous And a disc-shaped transmission part 4b made of a material made of a porous material such as silicon.

  The outer diameter of the non-transmissive portion 4a of the resistance plate 4 is the same as the outer diameter of the rubber ring 2 and the outer diameter of the rubber ring 3, and the inner diameter of the non-transmissive portion 4a and the outer diameter of the transmissive portion 4b are also equal. The inner diameter of the non-transmissive portion 4a is equal to the inner diameter of the rubber ring 2 and the inner diameter of the rubber ring 3. Further, the outer peripheral surface of the transmissive portion 4b is joined to the inner peripheral surface of the non-transmissive portion 4a of the resistance plate 4 by means such as welding.

  The two seal plates 5 are made of, for example, a melting agent such as iron or aluminum or a synthetic resin that does not allow the hydraulic oil and nitrogen gas constituting the fluid to pass therethrough. It is formed and formed in a disk shape having an outer diameter equal to the diameter. Below, the manufacturing process of the damper cell 1a is illustrated.

  First, the seal plate 5 is placed on the work table, and the lower surface of the rubber ring 3 is liquid-tightly bonded to the outer peripheral edge of the upper surface of the seal plate 5 by means such as vulcanization adhesion. At this stage, since the second fluid chamber B is defined on the inner peripheral side of the rubber ring 3, the second fluid chamber B is filled with hydraulic oil and nitrogen gas in a high-pressure chamber having a pressure higher than the atmospheric pressure. The

  Further, the lower surface of the non-transparent portion 4a of the resistance plate 4 is liquid-tightly joined to the upper surface of the rubber ring 3 by means of vulcanization adhesion or the like. On the other hand, the lower surface of the rubber ring 2 is joined in a liquid-tight manner by means such as vulcanization adhesion. At this stage, since the first fluid chamber A is defined on the inner peripheral side of the rubber ring 2, the first fluid chamber A is filled with hydraulic oil and nitrogen gas in the aforementioned high-pressure chamber.

  That is, the lower surface of the rubber ring 2 is liquid-tightly joined to the upper surface of the non-transmissive portion 4a of the resistance plate 4 by means such as vulcanization adhesion, and similarly, the upper surface of the rubber ring 3 is bonded to the lower surface of the non-transmissive portion 4a. Joined by means such as vulcanization bonding, the resistance plate 4 constitutes a sandwiched member that is fluid-tightly sandwiched between the rubber ring 2 and the rubber ring 3 in the predetermined axis C direction. Further, the outer peripheral edge portion of the upper surface of the lower seal plate 5 is liquid-tightly joined to the opposite side, that is, the lower surface of the resistance plate 4 of the rubber ring 3 by means of vulcanization adhesion or the like to constitute the second member. To do.

  After filling the first fluid chamber A with hydraulic oil and nitrogen gas from above the rubber ring 2 in the high-pressure chamber, the outer peripheral edge of the lower surface of the other seal plate 5 is attached to the resistance plate of the rubber ring 2. This is also liquid-tightly joined to the opposite side of 4, that is, the lower surface, by means such as vulcanization adhesion. That is, the other seal plate 5 located on the upper side constitutes a first member.

  As a result, the transmission part 4b of the resistance plate 4 is defined by the seal plate 5 as the first member, the rubber ring 2 as the first elastic member, and the resistance plate 4 as the sandwiched member, and is filled with fluid. The first fluid chamber A, the resistance plate 4 serving as a sandwiched member, the rubber ring 3 serving as the second elastic member, and the seal plate 5 serving as the second member are filled with the fluid. A throttle means is provided that communicates with the chamber B by imparting resistance to the fluid.

  Further, the seal plate 5, the rubber ring 3, the resistance plate 4, the rubber ring 2, and the other seal plate 5 are stacked in this order from the bottom to the top, and the first fluid chamber filled with fluid. The damper cell 1a which is a damping element is comprised by providing the A and 2nd fluid chamber B, and the expansion | swelling means which gives them resistance and communicates them.

  In addition to this, the predetermined axis C includes the vertical direction, and the rubber ring 2 as the first elastic member is positioned above the rubber ring 3 as the second elastic member so that the rubber ring 2 The rigidity of 2 is larger than the rigidity of the rubber ring 3. In this case, as shown in FIG. 3, since the outer diameter, inner diameter, and thickness in the predetermined axis C direction of the rubber ring 2 and the rubber ring 3 are the same, the elastic coefficient K2 of the rubber ring 2 is changed to the elastic coefficient of the rubber ring 3. The material of the rubber ring 2 and the rubber ring 3 is appropriately selected so as to be larger than K3.

  The seal plate 5 constituting the upper surface of the damper cell 1a configured as described above is also used as the lower seal plate 5 of the damper cell 1a adjacent to the upper side, and further, with respect to the outer peripheral edge of the upper surface of the seal plate 5 Then, the lower surface of the rubber ring 3 is joined in a liquid-tight manner by means such as vulcanization adhesion. At this stage, since the second second fluid chamber B is defined on the inner peripheral side of the rubber ring 3, the hydraulic oil and nitrogen gas are filled in the high-pressure chamber having a pressure higher than the atmospheric pressure.

  Further, the lower surface of the non-transparent portion 4a of the resistance plate 4 is liquid-tightly joined to the upper surface of the rubber ring 3 by means of vulcanization adhesion or the like. On the other hand, the lower surface of the rubber ring 2 is joined in a liquid-tight manner by means such as vulcanization adhesion. At this stage, since the second first fluid chamber A is defined on the inner peripheral side of the rubber ring 2, the hydraulic oil and nitrogen gas are filled in the high-pressure chamber described above. Hereinafter, by repeating these operations, as shown in FIG. 1, a shock absorber 1 in which five layers of damper cells 1a are stacked is configured.

  The seal plate 5 located on the uppermost side of the seal plate 5 constituting the shock absorber 1 is rigidly joined to the rod 60 by welding or bolting, and the seal plate 5 located on the lowermost side is welded or bolted to the knuckle 52. And so on.

  According to the damper cell 1a and the shock absorber 1 of the first embodiment configured as described above, the following operational effects can be obtained. That is, since the rigidity of the rubber ring 2 in the predetermined axis C direction is larger than the rigidity of the rubber ring 3 in the predetermined axis C direction, when an external force is applied in the predetermined axis C direction of the damper cell 1a, the predetermined axis C The deformation of the rubber ring 2 in the direction can be made smaller than the deformation of the rubber ring 3.

  Thereby, when the external force is applied in the direction of the predetermined axis C, the amount of change in the volume of the first fluid chamber A is made smaller than the amount of change in the volume of the second fluid chamber B, and the first fluid chamber B A fluid composed of hydraulic fluid and nitrogen gas can be moved to the fluid chamber A. As this fluid passes through the permeation part 4b, resistance is given by the fine holes of the porous body. Therefore, the damper cell 1a generates thermal energy based on the resistance of the fluid generated in the permeation part 4b to attenuate the vibration. A damping effect can be obtained.

  Similarly, when the external force no longer acts, the difference between the volume change amount of the first fluid chamber A and the volume change amount of the second fluid chamber B disappears, and the first fluid chamber A to the second fluid chamber. Since the fluid returns to B, resistance is given when the fluid passes through the transmission part 4b, and the damper cell 1a can obtain a damping effect that attenuates vibration based on the resistance of the fluid.

  Furthermore, since the rubber ring 2 and the rubber ring 3 constituting the damper cell 1a have a space for defining the first fluid chamber A and the second fluid chamber B on the inner peripheral side, the damper cell 1a is In the rubber ring 2 and the rubber ring 3 that enclose the predetermined axis C as compared with the case where the first fluid chamber A and the second fluid chamber B are not included and only the solid elastic member is configured, the predetermined axis By reducing the area in the cross section perpendicular to C, the rigidity in the direction of the predetermined axis C can be reduced.

  Thereby, the stroke as the damper cell 1a can be made larger. As a result, the stroke of the shock absorber 1 as a whole configured by stacking the damper cells 1a in the predetermined axis C direction can be increased.

  Moreover, the shock absorber 1 can be configured to have a greater damping effect by configuring the shock absorber 1 by stacking two or more damper cells 1a in the predetermined axis C direction. At the same time, when the external force acts on the rubber ring 2 and the rubber ring 3 as compared with the damper cell 1a including only the solid elastic member that does not include the first fluid chamber A and the second fluid chamber B. The effect of making the stroke of the shock absorber 1 larger by increasing the displacement in the predetermined axis C direction can be further enhanced.

  In addition, since the mechanical sliding portion can be eliminated as compared with the conventional telescopic shock absorber, it is possible to prevent the occurrence of hydraulic oil leakage due to the damage of the oil seal surface due to foreign matter contamination. . Similarly, it is possible to effectively prevent problems such as a foreign substance reaching the transmission part 4a constituting the diaphragm due to the mixing of the foreign substance and the damping force changing.

  Furthermore, in the shock absorber 1, the seal plate 5 that is the second member of the upper damper cell 1a and the seal plate 5 that is the first member of the lower damper cell 1a adjacent to each other in the direction of the predetermined axis C is made common. Accordingly, the components of one damper cell 1a adjacent in the direction of the predetermined axis C and the components of the other damper cell 1a can be partially shared, so that the number of parts of the shock absorber 1 as a damping device is reduced. be able to.

  In addition, the space occupied by the seal plate 5 in the direction of the predetermined axis C of the shock absorber 1 can be made as small as possible, and the volumes of the first fluid chamber A and the second fluid chamber B can be made as large as possible. The space inside the shock absorber 1 can be utilized as effectively as possible.

  In the first embodiment described above, the transmission part 4a using a porous body is used as the throttling means. However, the damping force generated by the transmission part 4a is the volume of the porous body with respect to the entire volume. It is possible to adjust by the specific gravity, which is an index indicating whether or not, and the thickness, that is, the dimension in the predetermined axis C direction, which is an index indicating the length of the term of the porous body. That is, when increasing the damping force, the specific gravity is increased as much as possible and the thickness is increased as much as possible.

  In addition, a plate having an appropriate number and diameter of holes is provided on the upper and lower surfaces of the transmission part 4a, and the number and diameter of the holes provided in the plate are adjusted so that the first fluid chamber A and the second fluid It is also possible to adjust the damping force generated by the transmission part 4a by adjusting the amount of fluid moving between the chamber B and the chamber B.

  The damper cell 1a, which is a damping element, can be assembled in the high-pressure chamber in units of the damper cell 1a, and the entire shock absorber 1 can be assembled at atmospheric pressure. The second embodiment will be described below.

  FIG. 4 is a schematic cross-sectional view showing another embodiment of the damping element and the damping device according to the present invention.

  Since the constituent elements constituting the damper cell 1a are the same as those shown in FIG. 3 of the first embodiment, overlapping explanations are omitted.

  First, the seal plate 5 is placed on the work table, and the lower surface of the rubber ring 3 is liquid-tightly bonded to the outer peripheral edge of the upper surface of the seal plate 5 by means such as vulcanization adhesion. At this stage, since the second fluid chamber B is defined on the inner peripheral side of the rubber ring 3, the hydraulic oil and nitrogen gas are filled in the high-pressure chamber having a pressure higher than the atmospheric pressure.

  Further, the lower surface of the non-transparent portion 4a of the resistance plate 4 is liquid-tightly joined to the upper surface of the rubber ring 3 by means of vulcanization adhesion or the like. On the other hand, the lower surface of the rubber ring 2 is joined in a liquid-tight manner by means such as vulcanization adhesion.

  At this stage, since the first fluid chamber A is defined on the inner peripheral side of the rubber ring 2, the hydraulic oil and nitrogen gas are filled in the above-described high-pressure chamber. On the other hand, the outer peripheral edge of the lower surface of another seal plate 5 is joined by means such as vulcanization adhesion.

  The damper cells 1a thus configured in the high-pressure chamber are stacked in five layers under atmospheric pressure, and the seal plates 5 of the damper cells 1a adjacent in the predetermined axis C direction are joined to each other by means of caulking or the like. Thus, the shock absorber 1 is configured.

  Also with the shock absorber 1 according to the second embodiment configured as described above, the same operational effects as those shown in the first embodiment can be obtained. At the same time, the seal plate 5 and the rubber ring 3, the rubber ring 3 and the resistance plate 4, the resistance plate 4 and the rubber ring 2, the rubber ring 2 and the seal plate 5 are joined to each other and sealed with hydraulic oil and nitrogen gas. The work is performed in units of damper cells 1a, and the shock absorber 1 can be assembled under atmospheric pressure conditions.

  That is, when the shock absorbers having different full lengths or stroke lengths are configured using the same damper cell 1a, the damper cells 1a which are parts can be shared, and the assembly work efficiency can be improved.

  In Example 1 and Example 2 described above, both the first member and the second member are made common as the seal plate 5 and the seal plate 5 is a disc-like one. You can also The third embodiment will be described below.

  FIG. 5 is a schematic cross-sectional view showing another embodiment of the damping element according to the present invention. As shown in FIG. 5, the damper cell 1 a includes a rubber ring 12, a rubber ring 13, a resistance plate 14, a seal plate 15, and a seal plate 16.

  Furthermore, as shown in FIG. 5, the seal plate 15 constituting the first member includes a cylindrical portion 15 a that offsets the surface including the predetermined axis C downward with respect to the outer peripheral edge portion, and the resistance constituting the sandwiched member In the plate 14, the non-transmissive portion 14a includes a cylindrical portion 14c for offsetting the transmissive portion 14b including the predetermined axis C downward with respect to the outer peripheral edge portion, and the predetermined axis of the seal plate 16 constituting the second member. The surface including C is offset downward with respect to the outer peripheral edge to include the cylindrical portion 16a. The transmission part 14b has the same configuration as that of the transmission part 4b shown in the first embodiment.

  Further, the outer diameter D1 of the cylindrical portion 15a and the inner diameter D2 of the cylindrical portion 14c are made equal, and the outer diameter D3 of the cylindrical portion 14c and the inner diameter D4 of the cylindrical portion 16a are made equal. That is, the outer peripheral surface of the cylindrical portion 15a and the inner peripheral surface of the cylindrical portion 14c constitute a first restricting means that restrains each other in the radial direction when the seal plate 15 and the resistance plate 14 are moved away from each other. The displacement between the seal plate 15 and the resistance plate 14 in the radial direction of the predetermined axis C is restricted when the seal plate 15 that constitutes the member and the resistance plate 14 that constitutes the member to be clamped approach and separate in the predetermined axis C direction.

  The outer peripheral surface of the cylindrical portion 14c and the inner peripheral surface of the cylindrical portion 16a constitute a second restricting means that restrains each other in the radial direction in the approaching / separating displacement between the resistance plate 14 and the seal plate 16; In the approaching / separating displacement in the predetermined axis C direction between the seal plate 16 constituting the two members and the resistance plate 14 constituting the sandwiched member, the displacement of the seal plate 16 and the resistance plate 14 in the radial direction of the predetermined axis C is regulated. To do.

  According to this, the relative displacement between the seal plate 15 and the resistance plate 14 and the relative displacement between the seal plate 16 and the resistance plate 14 in the radial direction of the predetermined axis C is suppressed, and the rubber constituting the first elastic member. Stroke direction when excessive force is applied to the ring 12 and the rubber ring 13 constituting the second elastic member in the radial direction, and force is applied to the damper cell 1a that is the damping element in the predetermined axis C direction. Can be stabilized.

  In the damper cell 1a of the third embodiment, the rigidity of the rubber ring 12 in the predetermined axis C direction is larger than the rigidity of the rubber ring 13 in the predetermined axis C direction as in the first embodiment. However, as shown in FIG. 5, the outer diameter D3 of the cylindrical portion 14c of the resistance plate 14 is set to be twice the thickness T of the seal plate 15 and the seal plate 16 rather than the outer diameter D1 of the cylindrical portion 15a of the seal plate 15. Since the area of the rubber ring 12 in the cross section perpendicular to the predetermined axis C is larger than the area of the rubber ring 13 in the cross section perpendicular to the predetermined axis C, the rigidity is increased in this case. In making the difference, the elastic coefficient K12 of the rubber ring 12 and the elastic coefficient K13 of the rubber ring 13 do not need to be different, and the same material can be used.

  Furthermore, instead of the first restricting means and the second restricting means as shown in the third embodiment, it is conceivable that the entire laminated damper cell 1a shown in the first or second embodiment is restrained by a cylinder from the outer peripheral side. In this case, a radial gap with the damper cell 1a is likely to be generated, and when the gap is generated, the regulation effect is small, so the configuration shown in the third embodiment is more advantageous.

  In Examples 1 to 3 described above, the non-permeable portions of the second member, the first elastic member, the second elastic member, and the sandwiched member are configured as separate parts, but a metal having a bellows structure is used. It is also possible to configure the damping element by integrally configuring them and joining the transmitting portion of the sandwiched member to the non-transmitting portion in a separate process. Hereinafter, Example 4 will be described.

  FIG. 6 is a schematic view showing another embodiment of the damping element according to the present invention. As shown in FIG. 6, the damper cell 1a of the fourth embodiment includes a metal body 17 having a two-stage bellows structure having a bottomed structure, and a transmission part 18 made of a porous body constituting a transmission part of the sandwiched member, And a seal plate 19 constituting the first member. The transmission part 18 has the same configuration as the transmission part 4b shown in the first embodiment and the transmission part 14b shown in the third embodiment.

  The metal body 17 is integrally formed to have a bottom surface and a side surface having a two-stage bellows structure by a hot rolling process, and the upper bellows portion 17a constitutes a first elastic member, and the lower bellows The portion 17b constitutes a second elastic member, the boundary portion 17c between the bellows portion 17a and the bellows portion 17b constitutes a non-permeable portion to which the transmissive portion 18 made of a porous body is joined, and the bottom portion 17d constitutes the second member. To do.

  Also, in the damper cell 1a of the fourth embodiment, the point that the rigidity of the bellows portion 17a in the predetermined axis C direction is made larger than the rigidity of the bellows portion 17b in the predetermined axis C direction is shown in the first to third embodiments. In this case, the thickness of the metal body 17 in the portion constituting the bellows portion 17a is made larger than the thickness of the metal body 17 constituting the bellows portion 17b, whereby the bellows portion 17a and the bellows 17 are formed. The rigidity of the part 17b is made different.

  The metal body 17 configured in this manner is filled with hydraulic oil and nitrogen gas in a high-pressure chamber and sealed, and the permeation portion 18 is liquid-tightly joined to the inner peripheral surface of the boundary portion 17c by welding or the like. The chamber is filled with hydraulic oil and nitrogen gas and sealed. Finally, the seal plate 19 is liquid-tightly joined to the upper opening of the metal body 17 by welding or the like.

  That is, the second fluid chamber B is defined by the bottom portion 17d, the bellows portion 17b, and the transmission portion 18, and the first fluid chamber A is defined by the transmission portion 18, the bellows portion 17a, and the seal plate 19. Also with the damper cell 1a of the fourth embodiment configured as described above, the same operational effects as those shown in the first embodiment can be obtained.

  Furthermore, according to the damper cell 1a of the fourth embodiment, the number of parts constituting the damper cell 1a is greatly reduced as compared with that shown in the first embodiment, and the working efficiency in constructing the damper cell 1a is increased. The manufacturing cost can be suppressed as much as possible.

  Note that a synthetic resin body having a bellows structure can be used instead of the metal body 17 having the bellows structure. In this case, in order to enhance the effect of sealing a fluid composed of hydraulic oil and nitrogen gas, It is preferable to form an impermeable film.

  Although the preferred embodiments of the present invention have been described in detail above, the present invention is not limited to the above-described embodiments, and various modifications and substitutions are made to the above-described embodiments without departing from the scope of the present invention. be able to.

  In addition, the damping device according to the present invention may be applied to a front suspension device of a vehicle in FIG. 1 or a rear suspension device. Of course, the suspension device to which the damping device according to the present invention is applied is not limited to being applied to the suspension device of the above-mentioned type, but other types of suspension devices such as a double wishbone type suspension device, a multi-link type suspension device, and the like. The present invention can also be applied to suspension devices, trailing arm type suspension devices, and the like.

  In addition, as to which of the shock absorbers 1 shown in the first and second embodiments is adopted, all the damper cells 1a are assembled in the high pressure chamber in the work process for configuring the shock absorber 1. If it is advantageous, it is advantageous to select the embodiment 1, and when it is advantageous to assemble the shock absorber 1 at atmospheric pressure after assembling only the damper cell 1a in the high-pressure chamber. It is preferable to select Example 2.

  In the above-described embodiment, the lower arm 54 is a so-called A arm. However, as long as the rigidity for supporting the wheels and the knuckle 52 can be secured, the lower arm 54 may have other shapes, such as an L arm and a U arm. It is also possible to use a Y arm or an I link.

  Further, in the above-described embodiment, the configuration in which the spring 53 is arranged on the same axis with respect to the shock absorber 1 is shown. However, if the spring 53 can be interposed between the shock absorber 1 and the vehicle body side, the same shaft is not necessarily used. It does not need to be configured on a line, and may be arranged on a separate axis.

  In the above-described embodiment, both the first fluid chamber A and the second fluid chamber B are filled and filled with hydraulic oil and nitrogen gas, but this may be changed as appropriate according to the required damping coefficient. It is possible to use only hydraulic oil or only nitrogen gas. Further, air or other gas can be used instead of nitrogen gas. In particular, hydraulic oil may be required to reduce the amount of use as much as possible from the viewpoint of environmental protection. In this case, it is preferable to increase the gas ratio.

  Further, in the above-described embodiment, the porous body is used as a means for imparting resistance to the fluid moving between the first fluid chamber A and the second fluid chamber B. Instead, an orifice or a choke is used. Is also possible. When an orifice is used, the damping force is adjusted by adjusting the diameter of the orifice. When a choke is used, the damping force is adjusted by adjusting the choke length.

  The present invention relates to a damping device suitable for being applied to a vehicle suspension device, and a relatively simple structure can provide a high damping effect and ensure a desired stroke. It is useful when applied to various vehicles such as trucks and buses.

It is a mimetic diagram showing one embodiment of a suspension device to which the damping device concerning the present invention is applied. It is a mimetic diagram showing one embodiment of an attenuation device concerning the present invention. It is a mimetic diagram showing one embodiment of an attenuation element concerning the present invention. It is a mimetic diagram showing one embodiment of an attenuation device concerning the present invention. It is a mimetic diagram showing one embodiment of an attenuation element concerning the present invention. It is a mimetic diagram showing one embodiment of an attenuation device concerning the present invention.

Explanation of symbols

1 Shock absorber (attenuator)
1a Damper cell (attenuating element)
2 Rubber ring 3 Rubber ring 4 Resistance plate 4a Non-transmission part 4b Transmission part 5 Seal plate 14 Resistance plate 14a Non-transmission part 14b Transmission part 14c Cylindrical part 15 Seal plate 15a Cylindrical part 16 Seal plate 16a Cylindrical part 17 Metal body 17a Bellows part 17b Bellows portion 17c Boundary portion 17d Bottom portion 18 Transmission portion 19 Seal plate 51 Suspension device 52 Knuckle 53 Spring 54 Lower arm 55 Tire 56 Wheel 57 Ball joint 58 Lower spring seat 59 Upper spring seat 60 Rod

Claims (7)

  A first elastic member and a second elastic member that are encased in a predetermined axis and are spaced apart from each other in a predetermined axial direction, and liquid-tight between the first elastic member and the second elastic member in the predetermined axial direction. A sandwiched member that is sandwiched between the first elastic member, a first member that is liquid-tightly joined to the opposite side of the sandwiched member of the first elastic member, and a liquid-tight member that is opposite to the sandwiched member of the second elastic member And a first fluid chamber in which the sandwiched member is defined by the first member, the first elastic member, and the sandwiched member and is filled with fluid, It comprises a throttle means for providing resistance to the fluid and communicating with the second fluid chamber defined by the sandwiched member, the second elastic member, and the second member and filled with fluid. A damping element.   The damping element according to claim 1, wherein the predetermined axis includes a vertical direction, and the first elastic member is positioned above the second elastic member.   The damping element according to claim 2, wherein the rigidity of the first elastic member is larger than the rigidity of the second elastic member in the predetermined axial direction.   4. A damping element according to claim 3, wherein the throttling means comprises an orifice, a choke or a porous body.   A first restricting means for restricting a displacement between the first member and the sandwiched member in a radial direction of the predetermined shaft upon the approaching / separating displacement of the first member and the sandwiched member in the predetermined axis direction; A second restricting means for restricting a displacement between the second member and the sandwiched member in a radial direction of the predetermined shaft when the second member and the sandwiched member are moved toward and away from each other in the predetermined axis direction; 5. Attenuating element according to claim 4, characterized in that   An attenuation device comprising: two or more of the attenuation elements according to claim 4 or 5 stacked in the predetermined axial direction.   The damping device according to claim 6, wherein the second member of the upper damping element and the first member of the lower damping element adjacent to each other in the predetermined axial direction are common.

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