JP2006226336A - Bushing - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a bushing capable of forcedly displacing an outer tube in a radial direction in relation to an inner tube according to the relative rotation of the outer tube and the inner tube. <P>SOLUTION: The bushing 10 is provided with the outer tube 11 and the inner tube 12, and further provided with rubber 13 (elastic body) between the outer tube 11 and the inner tube 12 as one unit. The outer tube 11 and the inner tube 12 as concentrically arranged to align an outer tube center axis Lo and an inner tube center axis Li of each axis. The rubber 13 is vulcanized on the inner circumference 11a of the outer tube 11 and the outer circumference of the inner tube 12 at the outer circumference and the inner circumference thereof, respectively. The rubber 13 has gaps 14, 15 passing through in an axial direction and permitting the elastic deformation of the rubber 13 formed thereon. A connecting member 16 (forced displacement means) is put between the outer tube and the inner tube 12. The connecting member 16 is fixed on the outer circumference 12a of the inner tube 12 at the inner end 16a thereof and fixed on the inner circumference 11a of the outer tube 11 at the outer end 16b thereof. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to a bush formed by interposing an elastic body such as rubber between an outer cylinder and an inner cylinder, for example, a bush used for a suspension device of a vehicle.

As this type of bush, there is an outer cylinder that is disposed on the outer periphery of the inner cylinder and is relatively rotatable about the circumferential direction of the inner cylinder, and an elastic body such as rubber is interposed between the inner cylinders, for example, It is described in the following Patent Document 1. In the bush described in Patent Document 1, the outer cylinder and the inner cylinder are arranged coaxially, and relative rotation between the outer cylinder and the inner cylinder is allowed according to the twist of the elastic body.
JP-A-8-320041

  By the way, in the above-mentioned bush of Patent Document 1, a gap extending in the circumferential direction is formed inside the elastic body, and a protrusion is located in the vicinity of the elastic body constituting one inner wall in the gap. Is fixed to the inner periphery of the outer cylinder. Therefore, during the relative rotation of the outer cylinder and the inner cylinder, if the protrusion does not contact the inner wall, only the reaction force due to the torsion of the elastic body is applied, but if the protrusion contacts the inner wall, the protrusion The pressing force is further applied as a reaction force. For this reason, the rigidity at the time of rotation changes according to the direction of relative rotation between the outer cylinder and the inner cylinder.

  However, in the bush described in Patent Document 1 described above, the rigidity at the time of rotation can be forcibly changed according to the relative rotation between the outer cylinder and the inner cylinder. The outer cylinder cannot be forcibly displaced in the radial direction with respect to the inner cylinder in accordance with the relative rotation.

  Therefore, in order to cope with the above-described problems, the present invention provides a bush capable of forcibly displacing the outer cylinder in the radial direction with respect to the inner cylinder in accordance with the relative rotation between the outer cylinder and the inner cylinder. Has that purpose.

  In order to achieve the above object, in the present invention, an elastic body such as rubber is interposed between the outer cylinder disposed on the outer periphery of the inner cylinder so as to be relatively rotatable about the circumferential direction of the inner cylinder and the inner cylinder. Forcibly displacing means for forcibly displacing the outer cylinder in the radial direction with respect to the inner cylinder between the outer cylinder and the inner cylinder in accordance with relative rotation between the outer cylinder and the inner cylinder. It is characterized by being provided.

  In carrying out the present invention, the forced displacement means is fixed to the inner periphery of the outer cylinder at the outer end and is fixed to the outer periphery of the inner cylinder at the inner end, and the outer cylinder and the inner cylinder It is also possible that the inner end portion is wound around the inner cylinder according to the relative rotation of the inner cylinder, and the outer cylinder is displaced in the radial direction with respect to the inner cylinder.

  In carrying out the present invention, the forcible displacement means includes any one of a cam and a cam follower fixed to the inner periphery of the outer cylinder, and a cam and a cam follower fixed to the outer periphery of the inner cylinder. Any one of them is provided, and is configured by a cam mechanism that engages according to relative rotation between the outer cylinder and the inner cylinder to displace the outer cylinder in the radial direction with respect to the inner cylinder. Is also possible.

  In carrying out the present invention, the forcible displacement means is a gear mechanism that advances meshing according to relative rotation between the outer cylinder and the inner cylinder to displace the outer cylinder in the radial direction with respect to the inner cylinder. It can also be configured. In this case, the gear mechanism includes an outer gear integrally provided on the outer periphery of the inner cylinder, a holder disposed on the outer periphery of the inner cylinder and engaged with the elastic body on the outer periphery, and an inner periphery of the holder And an inner gear that meshes with the outer gear, and the curvature of the outer gear can be set larger than the curvature of the inner gear. The gear mechanism includes an inner gear integrally provided on the inner periphery of the outer cylinder, a holder that is disposed on the outer periphery of the inner cylinder and engages with the elastic body on the inner periphery, and is integrated with the outer periphery of the holder. And an outer gear that meshes with the inner gear, and the curvature of the inner gear may be set smaller than the curvature of the outer gear.

  In this bush, the outer cylinder is forcibly displaced in the radial direction with respect to the inner cylinder by the forcible displacement means by the relative rotation of the outer cylinder and the inner cylinder. Thereby, the position adjustment using the relative displacement in the radial direction of the outer cylinder and the inner cylinder is possible when the bush is assembled.

  In implementing the present invention, the bush may be interposed at at least one end of a suspension arm that connects the vehicle body and the wheel support member. In this case, the suspension arm is forcibly displaced according to the rotation of the suspension arm by the bush provided with the forced displacement means. For this reason, it is possible to change the alignment according to the rotation of the suspension arm without changing the length and arrangement of the suspension arm.

  Hereinafter, each embodiment of the present invention will be described with reference to the drawings. FIG. 1 shows a bush 10 according to a first embodiment of the present invention. The bush 10 includes a cylindrical outer cylinder 11 and an inner cylinder 12, and an elastic body between the outer cylinder 11 and the inner cylinder 12. The rubber 13 is integrally provided. The outer cylinder 11 and the inner cylinder 12 are arranged coaxially so that the outer cylinder central axis Lo and the inner cylinder central axis Li, which are the respective axes, coincide with each other.

  The rubber 13 is interposed between the outer cylinder 11 and the inner cylinder 12, and is vulcanized and bonded to the inner periphery 11a of the outer cylinder 11 and the outer periphery 12a of the inner cylinder 12 at the outer periphery and inner periphery thereof. The rubber 13 is formed with gaps 14 and 15 (straight) that penetrate in the axial direction and allow elastic deformation of the rubber 13, and the outer cylinder 11 and the inner cylinder 12 are axially, radially, and around the axis. Relative displacement is possible.

  A connecting member 16 is interposed between the outer cylinder 11 and the inner cylinder 12. The connecting member 16 is formed in a predetermined band shape from a high-tensile material, for example, a steel thin plate, nylon fiber, Kevlar fiber, and the like, and is fixed to the outer periphery 12a of the inner cylinder 12 at the inner end 16a. The outer end 16b is fixed to the inner periphery 11a of the outer cylinder 11, and is arranged in an arc shape so as to follow the inner periphery of the gap 15 at the intermediate portion.

  In the bush 10 of the first embodiment configured as described above, for example, when the inner cylinder 12 is rotated clockwise with respect to the outer cylinder 11 with the outer cylinder 11 fixed, the inner end of the connecting member 16 The part starts to wind around the inner cylinder 12 (see FIG. 1B). As the amount of wrapping of the connecting member 16 around the inner cylinder 12 increases, the rubber 13 is deflected in the radial direction, and the gap 15 is crushed so that the inner cylinder 12 on the inner end 16a side of the connecting member 16 is crushed. Since the outer cylinder 11 approaches the outer cylinder 11, the inner cylinder central axis Li is displaced radially from the position of the outer cylinder central axis Lo (see FIG. 1C). Even when the outer cylinder 11 is rotated counterclockwise with respect to the inner cylinder 12 with the inner cylinder 12 fixed, the inner cylinder central axis Li and the outer cylinder central axis Lo can be made different as described above. it can. However, in this case, since the outer cylinder 11 on the side to which the outer end 16b of the connecting member 16 is fixed approaches the inner cylinder 12 as the connecting member 16 is wound around the inner cylinder 12, the center of the outer cylinder The axis Lo is displaced in the radial direction from the position of the inner cylinder central axis Li.

  Therefore, either one of the outer cylinder 11 and the inner cylinder 12 of the bush 10 according to the first embodiment is fixed to a wheel support member such as a vehicle body or a knuckle, and either the outer cylinder 11 or the inner cylinder 12 is used. If the other is assembled to the suspension arm, the distance and position between the vehicle body and the wheel support member can be changed according to the relative rotation of the outer cylinder 11 and the inner cylinder 12 during the assembly operation. The alignment of the toe angle, the camber angle, etc. can be adjusted without changing the length, arrangement, etc.

  Further, by applying the bush 10 of the first embodiment to the suspension arm constituting the vehicle suspension device, alignment is performed according to the rotation of the suspension arm without changing the length and arrangement of the suspension arm. It is also possible to change. 2 to 6 schematically illustrate the configuration and operation of a vehicle suspension apparatus in which the bush 10 of the first embodiment is applied to the lower arm 33 so that the toe angle is changed in accordance with the rotation of the lower arm 33. FIGS. 7 to 10 show the configuration of a vehicle suspension apparatus in which the bush 10 of the first embodiment is applied to the upper arm 32 and the camber angle is changed according to the rotation of the upper arm 32. The operation is schematically shown.

  First, the case where the bush 10 of 1st Embodiment is applied to the lower arm 33 is demonstrated based on FIGS. As shown in FIG. 2, the vehicle suspension apparatus including the lower arm 33 is of a double wishbone type, and a knuckle 31 (wheel support member) that rotatably supports a wheel 30 by a spindle 31a includes a suspension arm. Are connected to the vehicle body 50 by an A-shaped upper arm 32 and an A-shaped lower arm 33, and are also connected to a steering rack 35 via a tie rod 34.

  The upper arm 32 extends in the vehicle width direction, is connected to the upper portion of the knuckle 31 via a ball joint 36 at the outer end in the vehicle width direction, and is a known rubber bush at each inner end in the vehicle width direction. It is connected to the vehicle body 50 through 37. The lower arm 33 extends in the vehicle width direction, and is connected to the lower portion of the knuckle 31 via the ball joint 38 at the outer end in the vehicle width direction, and via the bush 10 at each inner end in the vehicle width direction. Are connected to the vehicle body 50.

  The tie rod 34 is connected to the front intermediate portion of the knuckle 31 via a ball joint 39 at the outer end in the vehicle width direction, and is connected to the steering rack 35 via the ball joint 41 at the inner end in the vehicle width direction. ing. The steering rack 35 displaces the tie rod 34 in the vehicle width direction by operating a handle (not shown), and rotates the knuckle 31 around the virtual kingpin axis. Note that the virtual kingpin axis is formed by a line connecting the ball centers of the ball joints 36 and 38.

  As shown in FIG. 3 (A), the bush 10 is press-fitted into a through hole 33a formed in the lower arm 33 in the outer cylinder 11, and the vehicle body 50 via a bolt (not shown) in the inner cylinder 12. The outer cylinder center axis Lo and the inner cylinder center axis Li extend in the horizontal direction. The connecting member 16 is disposed so that the inner end 16 a and the outer end 16 b thereof are positioned on the substantially longitudinal center line of the lower arm 33.

  When the bush 10 according to the first embodiment is applied to the lower arm 33 as described above, the bush 50 from the vehicle body 50 or the wheel 30 through the lower arm 33 when the wheel 30 is in the neutral position (FIG. 3A). When the force in the front-rear direction or the width direction of the vehicle is input to 10, the connecting member 16 is arranged in a curved state, so that the axial direction or diameter of the outer cylinder 11 relative to the inner cylinder 12 according to the bending of the rubber 13. Displacement in the direction is allowed.

  When the wheel 30 bounces from the neutral position and the lower arm 33 rotates counterclockwise about the inner cylinder central axis Li as an axis, the outer cylinder 11 rotates counterclockwise with respect to the inner cylinder 12, and the connecting member 16 The inner end portion starts to wrap around the inner cylinder 12 (FIG. 3B). For this reason, as the outer cylinder 11 on the side to which the outer end 16b of the connecting member 16 is fixed approaches the inner cylinder 12, the outer cylinder central axis Lo moves from the position of the inner cylinder central axis Li to the inner side in the longitudinal direction of the lower arm 33. Displace towards the direction. When the bound amount of the wheel 30 becomes maximum, the displacement amount D between the outer cylinder center axis Lo and the inner cylinder center axis Li becomes maximum (FIG. 3C). That is, as the wheel 30 bounces, the length from the inner cylinder central axis Li to the outer end in the vehicle width direction of the lower arm 33 is apparently reduced.

  For this reason, when the wheel 30 bounces, the ball center of the ball joint 38 between the lower arm 33 and the knuckle 31 is displaced inward in the vehicle width according to the displacement of the outer cylinder central axis Lo. At this time, since the tie rod 34 and the steering rack 35 are not displaced in the vehicle width direction, the ball center of the ball joint 39 between the tie rod 34 and the knuckle 31 is not displaced. Accordingly, the ball center of the ball joint 39 is pushed relatively outward in the vehicle width direction with respect to the ball center of the ball joint 38, and the wheel 30 is displaced in the toe-out direction.

  Accordingly, as shown by a solid line in FIG. 4, for example, when the positive toe angle (the toe angle in the toe-in direction) is set to increase as the bound amount of the wheel 30 increases, FIG. As indicated by broken lines, the negative toe angle (the toe angle in the toe-out direction) increases as the bound amount of the wheel 30 increases.

  Even if the wheel 30 rebounds from the neutral position and the lower arm 33 rotates clockwise around the inner cylinder central axis Li and the outer cylinder 11 rotates clockwise relative to the inner cylinder 12, the connecting member 16 The inner end of the inner cylinder 12 does not wind around the inner cylinder 12. Accordingly, since the outer cylinder center axis Lo and the inner cylinder center axis Li are kept in agreement with each other, the toe angle of the wheel 30 is rebounded according to the setting locus such as the arrangement and length of the lower arm 33. It changes accordingly (see FIG. 4).

  On the other hand, as shown in FIG. 5, when the bushing 10 is turned 180 ° around the axis from the assembled state of FIG. 3A and assembled to each inner end in the vehicle width direction of the lower arm 33, By winding around the inner cylinder 12, the outer cylinder center axis Lo is displaced from the position of the inner cylinder center axis Li toward the outer side in the longitudinal direction of the lower arm 33. That is, in this case, as the wheel 30 bounces, the length from the inner cylinder central axis Li to the outer end in the vehicle width direction of the lower arm 33 is apparently extended. For this reason, the ball center of the ball joint 39 is pulled relatively inward of the vehicle with respect to the ball center of the ball joint 38, and the wheels 30 are displaced in the toe-in direction.

  Thereby, as shown by a solid line in FIG. 6, for example, when the positive toe angle is set to increase as the bound amount of the wheel 30 increases, as shown by a broken line in FIG. 6, As the bounce amount of the wheel 30 increases, the positive toe angle further increases.

  Next, the case where the bush 10 of 1st Embodiment is applied to the upper arm 32 is demonstrated based on FIGS. In this case, the lower arm 33 is connected to the vehicle body 50 via a known rubber bush 37 at each inner end in the vehicle width direction. The other configuration of the vehicle suspension apparatus shown in FIG. 7 is the same as that of the vehicle suspension apparatus shown in FIG. .

  As shown in FIG. 8, the bush 10 is press-fitted into a through hole 32 a formed in the upper arm 32 in the outer cylinder 11, and is fixed to the vehicle body 50 through a bolt (not shown) in the inner cylinder 12. The outer cylinder center axis Lo and the inner cylinder center axis Li extend in the horizontal direction. The connecting member 16 is disposed such that the inner end 16 a and the outer end 16 b thereof are positioned on the substantially longitudinal center line of the upper arm 32.

  In the case where the bush 10 of the first embodiment is applied to the upper arm 32 as described above, when the wheel 30 bounces from the neutral position and the upper arm 32 rotates counterclockwise about the inner cylinder central axis Li, When the connecting member 16 is wound around the inner cylinder 12, the outer cylinder center axis Lo is displaced from the position of the inner cylinder center axis Li toward the inner side in the longitudinal direction of the upper arm 32.

  For this reason, when the wheel 30 bounces, the ball center of the ball joint 36 between the upper arm 32 and the knuckle 31 is displaced inward of the vehicle according to the displacement of the outer cylinder central axis Lo, but between the lower arm 33 and the knuckle 31. Since the ball center of the ball joint 38 can only be displaced in the vehicle width direction by a displacement amount corresponding to the setting locus such as the arrangement and length of the lower arm 33, the wheel 30 is displaced in the direction in which the negative camber angle increases. . As a result, as shown by the broken line from the state shown by the solid line in FIG. 9, the negative camber angle (the angle in the direction of falling to the inside of the vehicle) increases as the bound amount of the wheel 30 increases.

  On the other hand, when the bush 10 is turned 180 ° around the axis from the assembled state shown in FIG. 8 and assembled to each inner end in the vehicle width direction of the upper arm 32, the connection member 16 is wound around the inner cylinder 12, The outer cylinder center axis Lo is displaced outwardly in the longitudinal direction of the upper arm 32 from the position of the inner cylinder center axis Li.

  For this reason, when the wheel 30 bounces, the ball center of the ball joint 36 between the upper arm 32 and the knuckle 31 is displaced outwardly according to the displacement of the outer cylinder central axis Lo, but between the lower arm 33 and the knuckle 31. Since the ball center of the ball joint 38 can only be displaced in the vehicle width direction by a displacement amount corresponding to a set locus such as the arrangement and length of the lower arm 33, the wheel 30 is displaced in the direction in which the positive camber angle increases. . As a result, as shown by the broken line from the state shown by the solid line in FIG. 10, the positive camber angle (the angle in the direction of falling to the outside of the vehicle) increases as the bound amount of the wheel 30 increases.

  In the bush 10 according to the first embodiment, since the connecting member 16 is arranged in an arc shape between the outer cylinder 11 and the inner cylinder 12, the connecting member 16 is started from the initial relative rotation between the outer cylinder 11 and the inner cylinder 12. However, as shown in FIG. 11, the connecting member 16 is arranged between the outer cylinder 11 and the inner cylinder 12 in a state of being folded in a bellows shape. It is also possible. In this case, as shown in FIG. 12, when the relative rotation angle between the outer cylinder 11 and the inner cylinder 12 is smaller than the predetermined angle θ, the connecting member 16 does not wind around the inner cylinder 12, so that the outer cylinder central axis The amount of displacement between Lo and the inner cylinder center axis Li becomes zero, but when the angle is larger than the predetermined angle θ, the connecting member 16 winds around the inner cylinder 12, so that the outer cylinder center axis Lo and the inner cylinder center axis Li are The amount of displacement increases in proportion to the rotation angle.

  Moreover, in the bush 10 of the said 1st Embodiment and its deformation | transformation embodiment, although the case where one connection member 16 was used was demonstrated, as shown in FIG. ) Can also be used. In this case, since the effect of winding the connecting member 16 around the inner cylinder 12 is increased, the outer cylinder shaft Lo is moved in the radial direction with respect to the inner cylinder axis Li in accordance with the relative rotation between the outer cylinder 11 and the inner cylinder 12. It is possible to be surely displaced. Moreover, it is also possible to use a low-tensile material for each connecting member 16.

  In addition, in the bush 10 of the above-described first embodiment and each modified embodiment, the connecting member 16 is not limited to a band shape, and may be a string shape, for example, and the shape, number, arrangement, and the like can be changed as appropriate.

  In the bush 10 of the first embodiment and each modified embodiment described above, the connecting member 16 functions as a forced displacement means. However, instead of the connecting member 16, as shown in FIG. It is also possible to implement using. The other configuration of the bush 10 of the second embodiment shown in FIG. 14 is the same as that of the bush 10 of the first embodiment. Omitted.

  As shown in FIG. 14A, the cam mechanism C includes a cam 17 and a cam follower 18. The cam 17 and the cam follower 18 constitute a flat cam, are formed in a contour shape having convex arcs that can be engaged with each other, and are formed of a highly rigid material such as steel or aluminum alloy. . When the outer cylinder 11 is fixed, the cam 17 is fixed to the outer periphery 12 a of the inner cylinder 12 and the cam follower 18 is fixed to the inner periphery 11 a of the outer cylinder 11. On the other hand, when the inner cylinder 12 is fixed, the cam 17 is fixed to the inner periphery 11 a of the outer cylinder 11 and the cam follower 18 is fixed to the outer periphery 12 a of the inner cylinder 12.

  In the bush 10 of the second embodiment configured as described above, for example, when the inner cylinder 12 is rotated clockwise with respect to the outer cylinder 11 with the outer cylinder 11 fixed, the cam 17 and the cam follower 18 are rotated. Engagement begins (see FIG. 14B). As this engagement proceeds, the rubber 13 is deflected in the radial direction, and the gap 15 is crushed and the inner cylinder 12 is separated from the outer cylinder 11 on the cam follower 18 side. It is displaced in the radial direction from the position of the central axis Lo (see FIG. 14C). Even when the outer cylinder 11 is rotated counterclockwise with respect to the inner cylinder 12 with the inner cylinder 12 fixed, the inner cylinder central axis Li and the outer cylinder central axis Lo can be made different as described above. it can. However, in this case, the outer cylinder center axis Lo is displaced in the radial direction from the position of the inner cylinder center axis Li by the engagement of the cam 17 and the cam follower 18.

  Therefore, either one of the outer cylinder 11 and the inner cylinder 12 of the bush 10 according to the second embodiment is fixed to a wheel support member such as a vehicle body or a knuckle, and either the outer cylinder 11 or the inner cylinder 12 is used. If the other is assembled to the suspension arm, the alignment can be adjusted according to the relative rotation of the outer cylinder 11 and the inner cylinder 12 during the assembling work, as in the case of the bush 10 of the first embodiment described above. It is.

  Further, by applying the bush 10 of the second embodiment to the lower arm 33, the toe angle can be changed according to the rotation of the lower arm 33, as in the case of the bush 10 of the first embodiment described above. By applying to the upper arm 32, the camber angle can be changed according to the rotation of the upper arm 32.

  In the above-described bush 10 of the second embodiment, the case where the cam mechanism C includes the pair of cams 17 and the cam follower 18 has been described. For example, as illustrated in FIG. 15, the cam mechanism C includes the cam 17 and the cam follower 18. Are provided with a plurality of them (in FIG. 15, either one of the cam 17 and the cam follower 18 is two, and one of the cam 17 and the cam follower 18 is one). Is also possible. In this case, for example, even if the outer cylinder 11 is rotated clockwise or counterclockwise with respect to the inner cylinder 12 while the inner cylinder 12 is fixed, the outer cylinder center axis Lo remains at the inner cylinder center. It can be displaced in the radial direction (downward in FIG. 15) from the position of the axis Li. In addition, it is also possible not to provide the space | gap 15 by using a soft thing as the rubber | gum 13. FIG.

  Further, for example, as shown in FIG. 16, it is possible to provide a plurality of cams 17 and cam followers 18 (two cams 17 and two cam followers 18 in FIG. 16). In this case, for example, when the outer cylinder 11 is rotated clockwise with respect to the inner cylinder 12 with the inner cylinder 12 fixed, the outer cylinder central axis Lo is moved radially from the position of the inner cylinder central axis Li ( 16 can be displaced downward (in FIG. 16), and when rotated counterclockwise, the outer cylinder central axis Lo is displaced in the radial direction (upward in FIG. 16) from the position of the inner cylinder central axis Li. be able to.

  In the bush 10 of the second embodiment and each modified embodiment described above, the shape, number, arrangement, and the like of the cam 17 and the cam follower 18 constituting the cam mechanism C can be changed as appropriate.

  In the bushes 10 of the first and second embodiments and the modified embodiments described above, the connecting member 16 and the cam mechanism C function as forced displacement means, respectively. Instead, for example, as shown in FIG. 17, it is also possible to use a gear mechanism G1. In addition, since the other structure of this 3rd Embodiment shown in FIG. 17 is the same as that of the said 1st Embodiment, the same code | symbol is attached | subjected to the same member and description is abbreviate | omitted.

  As shown in FIG. 17A, the gear mechanism G1 includes an outer gear 21 provided integrally with the outer periphery of the inner cylinder 12, and an inner gear 23 provided on the inner periphery of the holder 22. The outer gear 21 is provided along the outer periphery of the inner cylinder 12, and is formed such that the curvature of the pitch circle is substantially equal to the curvature of the inner cylinder 12.

  The holder 22 has a rectangular cylindrical shape, is disposed on the outer periphery of the inner cylinder 12 so as to be allowed to slide with the inner cylinder 12, and is vulcanized and bonded to the rubber 13 on the outer periphery. The inner gear 23 is formed in a rack tooth shape in which the curvature of the pitch line is smaller than the curvature of the pitch circle of the outer gear 21, and is provided in the radial direction along the inner periphery of the holder 22 and meshes with the outer gear 21.

  In the bush 10 of the third embodiment configured as described above, for example, when the inner cylinder 12 is rotated counterclockwise with respect to the outer cylinder 11 with the outer cylinder 11 fixed, the inner gear of the outer gear 21 is obtained. As the meshing with 23 progresses, the inner cylinder center axis Li is displaced radially from the position of the outer cylinder center axis Lo while the inner cylinder 12 is guided to the inner circumference of the holder 22 (FIGS. 14B and 14). (See (C)). In this case, the gaps C1 and C2 (see FIG. 14A) between the inner cylinder 12 and the holder 22 are set to a predetermined size so that the outer cylinder 11 and the inner cylinder 12 are rotated in the direction of relative rotation. Accordingly, it is possible to set different amounts of displacement in the radial direction between the outer cylinder shaft Lo and the inner cylinder shaft Li.

  Even if the outer cylinder 11 is rotated clockwise with respect to the inner cylinder 12 with the inner cylinder 12 fixed, the inner cylinder central axis Li and the outer cylinder central axis Lo can be made different from each other as described above. . However, in this case, as the meshing of the inner gear 23 with the outer gear 21 proceeds, the outer cylinder center axis Lo is displaced in the radial direction from the position of the inner cylinder center axis Li.

  Therefore, if one of the outer cylinder 11 and the inner cylinder 12 of the bush 10 of the third embodiment is fixed to a wheel support member such as a vehicle body or a knuckle, and the other is assembled to a suspension arm, the above Similar to the bush 10 of the first embodiment, the alignment can be adjusted according to the relative rotation of the outer cylinder 11 and the inner cylinder 12 during the assembly operation.

  Further, by applying the bush 10 of the third embodiment to the lower arm 33, the toe angle can be changed according to the rotation of the lower arm 33, as in the case of the bush 10 of the first embodiment described above. By applying to the upper arm 32, the camber angle can be changed according to the rotation of the upper arm 32.

  In the bush 10 of the third embodiment described above, the case where the gear mechanism G1 is applied to a bush of a type in which the outer cylinder 11 is formed in a cylindrical shape has been described. For example, as shown in FIG. For the bush of the type formed in a rectangular shape, it is possible to obtain the same effect as the bush 10 of the third embodiment described above by applying the gear mechanism G2.

  As shown in FIG. 18, the gear mechanism G <b> 2 includes an inner gear 23 provided integrally on the inner periphery of the outer cylinder 11 and an outer gear 21 provided on the outer periphery of the holder 22. The inner gear 23 is formed in a rack tooth shape, and is provided in the radial direction along the inner periphery of the outer cylinder 11.

  The holder 22 has a cylindrical shape, is disposed on the inner periphery of the outer tube 11 so as to be allowed to slide with the outer tube 11, and is vulcanized and bonded to the rubber 13 on the inner periphery. The outer gear 21 is provided along the outer periphery of the holder 22 so that the curvature of the pitch circle is substantially equal to the curvature of the holder 22 and is larger than the curvature of the pitch line of the inner gear 23. It is formed and meshes with the inner gear 23.

  In the bush 10 according to the modified embodiment configured as described above, the outer cylinder 11 can be rotated counterclockwise or clockwise with respect to the inner cylinder 12 with the inner cylinder 12 fixed. As the meshing of the inner gear 23 with the outer gear 21 proceeds, the outer cylinder center axis Lo is displaced in the radial direction from the position of the inner cylinder center axis Li.

  In the above description, when the bush 10 according to the first to third embodiments is applied to the lower arm 33 or the upper arm 32, the inner cylinder 12 is fixed to the vehicle body 50, and the outer cylinder 11 is a vehicle of the lower arm 33 or the upper arm 32. The outer cylinder 11 is fixed to the vehicle body 50 and the inner cylinder 12 is assembled to each inner end in the vehicle width direction of the lower arm 33 or the upper arm 32. It is also possible to do.

  Further, in the first to third embodiments described above, the outer cylinder 11 is fitted into a through hole 33a or a through hole 32a formed at each inner end in the vehicle width direction of the lower arm 33 or the upper arm 32, and the lower arm 33 or the upper arm is fitted. For example, FIG. 19 shows the bush 10 according to the third embodiment as a representative, and FIG. 20 shows a modified embodiment of the third embodiment. As representatively shown by the bush 10, the outer cylinder 11 can be applied to a bush of a type that is fixed to the inner end of the lower arm or the upper arm.

  In the first to third embodiments described above, the case where the bush 10 is interposed at the inner end of the lower arm 33 or the upper arm 32 has been described. However, the bush 10 is interposed at the outer end of the lower arm 33 or the upper arm 32 or the like. It is also possible to interpose at both ends of the lower arm 33 or the upper arm 32 or the like.

  In the first to third embodiments described above, the case where the bush 10 is applied to the suspension arm such as the lower arm 33 or the upper arm 32 has been described. However, the bush 10 may be applied to a vehicle body connection member other than the suspension arm. is there.

FIG. 1 (A) is a side sectional view showing a first embodiment of a bush according to the present invention, and FIGS. 1 (B) and 1 (C) show the operation of the bush shown in FIG. 1 (A). It is side surface sectional drawing. It is a perspective view which shows roughly the right front-wheel side of the suspension apparatus containing the lower arm to which the bush concerning 1st Embodiment of this invention is applied with a skeleton. 3A is a partially cutaway side view showing a state in which the bush shown in FIG. 1 is assembled to the lower arm shown in FIG. 2, and FIG. 3B and FIG. It is a partially broken side view which shows the effect | action of the bush shown to A). FIG. 4 is an explanatory diagram showing a system between a bounce amount of the right front wheel and a toe angle when the bush is assembled to the lower arm as shown in FIG. 3. FIG. 4 is a partially cutaway side view showing a state in which the bush shown in FIG. 1 is assembled to the lower arm shown in FIG. 2 in a manner different from the assembly manner shown in FIG. 3. FIG. 6 is an explanatory diagram showing the relationship between the bounce amount of the right front wheel and the toe angle when the bush is assembled to the lower arm as shown in FIG. 5. It is a perspective view which shows roughly the right front-wheel side of the suspension apparatus containing the upper arm to which the bush concerning 1st Embodiment of this invention is applied with a skeleton. FIG. 3 is a partially cutaway side view showing a state in which the bush shown in FIG. 1 is assembled to the upper arm shown in FIG. 2. It is explanatory drawing which shows the relationship between the bounce amount of a right front wheel when a bush is assembled | attached to an upper arm as shown in FIG. 8, and a camber angle | corner. It is explanatory drawing which shows the relationship between the bounce amount of a right front wheel, and a camber angle | corner when the bush shown in FIG. 1 is assembled | attached to the upper arm shown in FIG. 2 in the aspect different from the assembly | attachment aspect shown in FIG. It is side surface sectional drawing which shows the deformation | transformation embodiment of the bush which concerns on 1st Embodiment shown in FIG. It is explanatory drawing which shows the relationship between the displacement amount with respect to the inner cylinder central axis of the outer cylinder central axis in the bush shown in FIG. 11, and the relative rotation angle with respect to the inner cylinder of an outer cylinder. It is side surface sectional drawing which shows another deformation | transformation embodiment of the bush which concerns on 1st Embodiment shown in FIG. 14A is a side sectional view showing a second embodiment of the bush according to the present invention, and FIGS. 14B and 14C show the operation of the bush shown in FIG. 14A. It is side surface sectional drawing. It is side surface sectional drawing which shows the deformation | transformation embodiment of the bush which concerns on 2nd Embodiment shown in FIG. It is side surface sectional drawing which shows another deformation | transformation embodiment of the bush which concerns on 2nd Embodiment shown in FIG. FIG. 17 (A) is a side sectional view showing a third embodiment of the bush according to the present invention, and FIGS. 17 (B) and 17 (C) show the operation of the bush shown in FIG. 17 (A). It is side surface sectional drawing. It is side surface sectional drawing which shows the deformation | transformation embodiment of the bush which concerns on 3rd Embodiment shown in FIG. FIG. 3 is a partially cutaway side view showing an example in which the bush according to the present embodiment is applied to a suspension arm of a type different from the lower arm and the upper arm shown in FIG. 2. It is a partially broken side view which shows an example at the time of applying the deformation | transformation embodiment of the bush concerning 3rd Embodiment to the suspension arm of a type different from the lower arm and upper arm shown in FIG.

Explanation of symbols

DESCRIPTION OF SYMBOLS 10 ... Bush, 11 ... Outer cylinder, 12 ... Inner cylinder, 13 ... Rubber (elastic body), Lo ... Outer cylinder center axis, Li ... Inner cylinder center axis, 14, 15 ... Gap, 16 ... Connecting member (forced displacement means) ), C ... cam mechanism (forced displacement means), 17 ... cam, 18 ... cam follower, G1, G2 ... gear mechanism (forced displacement means), 21 ... outer gear, 22 ... holder, 2
DESCRIPTION OF SYMBOLS 3 ... Inner gear, 30 ... Wheel, 31 ... Knuckle (wheel support member), 32 ... Upper arm, 33 ... Lower arm, 50 ... Car body

Claims (7)

In the bush that is arranged on the outer periphery of the inner cylinder and is relatively rotatable about the circumferential direction of the inner cylinder and an elastic body such as rubber interposed between the inner cylinders,
Forced displacement means is provided between the outer cylinder and the inner cylinder to forcibly displace the outer cylinder relative to the inner cylinder in response to relative rotation between the outer cylinder and the inner cylinder. Bush characterized by that. The bush according to claim 1,
The forced displacement means is fixed to the inner periphery of the outer cylinder at the outer end and fixed to the outer periphery of the inner cylinder at the inner end, and the inner end according to relative rotation between the outer cylinder and the inner cylinder. A bush comprising: a connecting member that wraps around the inner cylinder to displace the outer cylinder in a radial direction with respect to the inner cylinder. The bush according to claim 1,
The forced displacement means includes any one of a cam and a cam follower fixed to the inner periphery of the outer cylinder, and one of the cam and the cam follower fixed to the outer periphery of the inner cylinder. A bush comprising: a cam mechanism that engages according to relative rotation between the outer cylinder and the inner cylinder to displace the outer cylinder in a radial direction with respect to the inner cylinder. The bush according to claim 1,
The forced displacement means is configured by a gear mechanism that advances meshing according to relative rotation between the outer cylinder and the inner cylinder to displace the outer cylinder in a radial direction with respect to the inner cylinder. Bush to do. The bush according to claim 4,
The gear mechanism includes an outer gear that is integrally provided on the outer periphery of the inner cylinder, a holder that is disposed on the outer periphery of the inner cylinder and engages with the elastic body on the outer periphery, and is integrally provided on the inner periphery of the holder. And an inner gear that meshes with the outer gear, and the curvature of the outer gear is set larger than the curvature of the inner gear. The bush according to claim 4,
The gear mechanism includes an inner gear provided integrally on the inner periphery of the outer cylinder, a holder disposed on the outer periphery of the inner cylinder and engaged with the elastic body on the inner periphery, and integrally formed on the outer periphery of the holder. And an outer gear that meshes with the inner gear, and the curvature of the inner gear is set to be smaller than the curvature of the outer gear. In the bush according to any one of claims 1 to 6,
The bush is interposed in at least one end of a suspension arm that connects a vehicle body and a wheel support member.

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