JP6437739B2 - Suspension mechanism - Google Patents

Description

  The present invention relates to a suspension mechanism, and more particularly to a suspension mechanism that can ensure vibration damping performance and improve durability.

  In many suspension mechanisms of vehicles such as automobiles, the upper end of a shock absorber whose lower end is connected to the wheel side is connected to the body frame side via a mounting device, so that the wheel is swung up and down with respect to the body frame. Suspend movably. In the suspension mechanism, a spring seat rubber is interposed between an upper end portion of a coil spring that is externally fitted to the shock absorber and a receiving seat (flange portion) of the mount device (for example, Patent Document 1). The spring seat rubber is composed of a rubber-like elastic body, has an annular main body portion viewed in the axial direction, and an overhang portion formed by projecting radially outward from one outer peripheral side of the main body portion in the axial direction. It has. Vibration transmitted from the wheel side to the vehicle body frame side via the shock absorber is reduced by the mounting device, and vibration transmitted from the wheel side to the vehicle body frame side via the coil spring is reduced by the spring seat rubber.

JP 2009-210075 A

  However, in the above-described technique, when the spring seat rubber receives an axial load from the coil spring, the overhanging portion of the spring seat rubber is elastically deformed and spreads outward in the radial direction, and may ride on the flange portion of the mounting device. It was. If it does so, since the overhang | projection part will contact the edge of a flange part and it will become easy to damage, there existed a possibility that durability of a spring seat rubber might fall.

  If the overhanging portion is elastically deformed and spreads outward in the radial direction, the rubber volume of the overhanging portion interposed between the flange portion of the mounting device and the end of the coil spring is reduced, so that the rigidity is increased. As a result, the vibration damping performance of the spring seat rubber may be reduced.

  The present invention has been made to solve the above-described problems, and an object of the present invention is to provide a suspension mechanism that can ensure vibration damping performance and improve durability.

Means for Solving the Problems and Effects of the Invention

  In order to achieve this object, a suspension mechanism according to claim 1 includes a mount device having a flange portion connected to a cylindrical inner fitting portion, and a gap between the flange portion of the mount device and the end portion of the coil spring. A spring seat rubber composed of a rubber-like elastic body interposed. The spring seat rubber projects outwardly in the radial direction from the outer peripheral side on one end side in the axial direction of the annular main body portion when viewed in the axial direction to form an overhang portion. The main body portion and the overhang portion have a contact surface located on one end side in the axial direction in contact with the flange portion of the mounting device, a pressure receiving surface located on the other end side in the axial direction faces the contact surface, and a coil spring Take the end of the. The abutment surface comes into contact with the flange portion of the mounting device when the main body portion is fitted to the internal fitting portion of the mounting device and no load is received from the coil spring while no load is applied. A gap forming portion located on the radially outer side of the contact portion forms a gap with the flange portion of the mounting device.

  When the pressure receiving surface receives an axial load from the coil spring, the contact surface facing the pressure receiving surface is elastically deformed. Since the main body portion is fitted to the inner fitting portion of the mounting device, the elastic deformation inward in the radial direction of the contact surface is limited by the inner fitting portion. Therefore, the contact surface is elastically deformed toward the outside in the axial direction and the radial direction. Since the gap forming part located on the radially outer side of the contact part has a gap with the flange part, it is deformed in the axial direction more than the contact part. As a result, since the amount of elastic deformation of the gap forming portion radially outward can be reduced, it is difficult to ride the gap forming portion on the flange portion of the mounting device. Since interference between the flange portion and the overhang portion can be suppressed, there is an effect that the durability of the spring seat rubber can be improved.

Further, since the amount of elastic deformation of the gap forming portion radially outward can be reduced, it is possible to secure the rubber volume of the overhanging portion interposed between the flange portion of the mounting device and the end portion of the coil spring. Therefore, there is an effect that the damping performance can be secured.
The continuous portion of the flange portion with which the contact portion abuts is located on the other end side in the axial direction with respect to the flange portion where the gap forming portion abuts when receiving the axial load from the coil spring. Since the gap between the gap forming portion and the flange portion can be increased by an amount corresponding to the continuous portion as compared with a flat flange portion having no continuous portion, the amount of axial displacement of the gap forming portion can be increased. As a result, when the axial load is input from the coil spring, the amount of diameter expansion of the overhanging portion to the outside in the radial direction can be suppressed, and the rigidity of the overhanging portion can be prevented from becoming excessive.

  According to the suspension mechanism of the second aspect, at least a part of the gap forming portion is located on the radially outer side of the virtual first cylinder in which the outer periphery of the main body portion is extended in the axial direction when there is no load. When the pressure receiving surface receives an axial load from a coil spring whose end is disposed on the outer periphery of the main body, the gap forming portion positioned on the radially outer side of the first cylinder is elastically deformed in the axial direction. As a result, the rubber volume of the overhanging portion interposed between the flange portion of the mount device and the end portion of the coil spring can be secured, so that an increase in the axial rigidity of the spring seat rubber can be suppressed. Therefore, in addition to the effect of claim 1, there is an effect that the vibration damping performance can be improved.

According to the suspension mechanism of the third aspect, the main body portion is provided with the concave portion from the radially inner end portion of the contact portion toward the other end side in the axial direction. In the gap forming portion, the portion located on the outer side in the radial direction of the recess is continuous with the portion located on both sides in the circumferential direction of the portion . Thereby, when the spring seat rubber is attached to the mounting device, a space is formed by the recess between the inner fitting portion and the inner periphery of the main body portion. When an axial load is applied to the spring seat rubber, a part of the elastically deformed spring seat rubber can be accommodated in the space formed by the recess. Thereby, since the whole spring seat rubber can be elastically deformed substantially uniformly, it can prevent that a big load acts on a spring seat rubber locally. As a result, in addition to the effect of claim 1 or 2, the durability of the spring seat rubber can be improved.

  According to the suspension mechanism of the fourth aspect, the contact surface is formed with a plurality of recessed grooves that are recessed toward the other end side in the axial direction over the entire length in the radial direction. The recess is disposed between the plurality of grooves. In addition to the effect of the third aspect, the spring constant of the protruding portion can be adjusted by the concave groove.

  According to the suspension mechanism of the fifth aspect, the cylindrical fitting embedded in the other end side in the axial direction of the main body portion includes a cylindrical portion formed in a cylindrical shape and a radial direction from one end side in the axial direction of the cylindrical portion. And an eaves part that protrudes outwardly in a hook shape and is formed in a hook shape. The thickness of the main body portion and the overhang portion between the flange portion and the pressure receiving surface is set larger than the thickness of the main body portion on the pressure receiving surface side with respect to the cylindrical portion. Thereby, since a collar part approaches a clearance gap formation part and the elastic deformation to the radial direction outer side of a clearance gap formation part becomes easy to be prevented by a collar part, a clearance gap formation part cannot be spread easily to a radial direction outer side. As a result, in addition to the effect of any one of claims 1 to 4, the rubber volume of the overhanging portion between the flange portion and the coil spring is secured to improve the vibration damping performance of the spring seat rubber, and The durability of the spring seat rubber can be improved by making it difficult to ride the overhang on the flange.

It is an axial sectional view of the spring seat rubber in the first embodiment attached to the mounting device. It is a perspective view of a spring seat rubber. It is a top view of a spring seat rubber. It is a bottom view of a mounting device. It is an axial sectional view of the spring seat rubber attached to the mounting device. It is an axial sectional view of a spring seat rubber when receiving a load from a coil spring. It is an axial sectional view of a spring seat rubber in a second embodiment. It is an axial sectional view of a spring seat rubber in a third embodiment.

  DESCRIPTION OF EXEMPLARY EMBODIMENTS Hereinafter, preferred embodiments of the invention will be described with reference to the accompanying drawings. FIG. 1 is a sectional view in the axial direction of a spring seat rubber 1 according to the first embodiment attached to a mounting device 100. The spring seat rubber 1 shown in FIG. 1 is attached to the mounting bracket 101 of the mounting apparatus 100, but shows a state in which no load is received from the coil spring 107 in the axial direction. The mounting device 100 is provided with an anti-vibration base composed of a rubber-like elastic body between two mounting brackets. In FIG. 1, in order to simplify the drawing and facilitate understanding, The other mounting bracket 101 and the vibration-proof base are not shown.

  As shown in FIG. 1, the mounting bracket 101 of the mounting device 100 to which the spring seat rubber 1 is attached includes an inner fitting portion 102 formed in a cylindrical shape and one end side in the axial direction of the inner fitting portion 102 (upper side in FIG. 1). And a flange portion 103 that extends radially outward from the outer peripheral side of the end portion and is provided in an annular shape, and is a member that is connected to the body frame (not shown) side. Further, the mounting device 100 includes a ring-shaped partition portion 105 projecting radially inward from the inner peripheral surface of the inner fitting portion 102 of the mounting bracket 101, and the other end side in the axial direction (fixed to the partition portion 105). And a collar 106 protruding toward the lower side of FIG. The inner fitting portion 102 and the flange portion 103 are integrally formed of a metal material, and the connecting portion 104 (a part of the flange portion 103) in which the flange portion 103 is provided continuously with the inner fitting portion 102 is provided in the axial direction. It is a ring-shaped part having a flat surface entering the end side (lower side in FIG. 1).

  The spring seat rubber 1 is a member for reducing vibrations transmitted from the wheel (not shown) side to the vehicle body (not shown) side via the coil spring 107 and has a substantially cylindrical shape having an axis O. A main body portion 10 formed, and an overhang portion 20 that protrudes in a flange shape from the one end side (upper end portion in FIG. 1) in the axial direction of the main body portion 10 to the outer side in the axial direction. Yes. The main body portion 10 and the overhang portion 20 are integrally vulcanized from a rubber-like elastic body having an appropriate spring constant.

  The main body 10 is a portion where the inner fitting portion 102 of the mounting device 100 is fitted on the inner circumference 10 a side, and has an outer diameter that can be fitted to the inner circumference of the coil spring 107. The main body portion 10 prevents interference between the coil spring 107 and the inner fitting portion 102. The main body 10 is formed such that the diameter (inner diameter) of the inner periphery 10a gradually decreases as it goes toward the other end side in the axial direction (the lower side in FIG. 1). The diameter (outer diameter) of the outer periphery 10b of the main body 10 extends in the axial direction except that it is set smaller at the small diameter portion 11 located at the axial end on the other axial end (lower side in FIG. 1). Are set approximately the same. The small diameter portion 11 is formed so that the radial thickness is thinner than the radial thickness of the main body portion 10 (excluding the axial end portion).

  The overhang portion 20 is a portion interposed between the coil spring 107 and the flange portion 103 in order to prevent interference between the coil spring 107 and the flange portion 103 of the mounting apparatus 100. Vibration input from the coil spring 107 to the vehicle body (not shown) is suppressed by the main body portion 10 and the overhang portion 20. The overhang portion 20 is configured as a contact surface 21 configured as a surface coupled to the inner periphery 10 a of the main body portion 10 and a flat surface opposed to the contact surface 21 and coupled to the main body portion 10. The pressure receiving surface 22 is provided.

  A cylindrical fitting 30 is embedded in the main body portion 10 and the overhang portion 20. The cylindrical metal fitting 30 is a member formed from a metal material, and protrudes radially outward from a cylindrical portion 31 formed in a cylindrical shape and one axial end side (upper end portion in FIG. 1) of the cylindrical portion 31. And a flange 32 formed in a bowl shape. The cylindrical portion 31 has an axial length that is set to a length obtained by adding approximately ½ of the axial thickness of the overhang portion 20 to the axial length of the main body portion 10. It forms so that it may become small gradually as it goes to an end side (lower side of FIG. 1).

  The eaves part 32 is embedded in the center of the overhang part 20 in the axial direction. Increasing the rigidity of the portion where the cylindrical portion 31 is embedded (the axial end portion of the main body portion 10) by embedding the cylindrical portion 31 on the end portion side in the axial direction of the main body portion 10 (lower side in FIG. 1). Can do. As a result, the axial position of the main body portion 10 is prevented from shifting from the inner fitting portion 102 toward the flange portion 103 by the input of the axial load to the pressure receiving surface 22 by the coil spring 107, and the spring seat rubber 1 from the mounting device 100 is prevented. Can prevent drowning and falling off.

  The collar portion 32 is coupled to the cylindrical portion 31 and is embedded in the overhang portion 20. The flange portion 32 is disposed between the flange portion 103 and the end portion of the coil spring 107, and the cylindrical portion 31 is disposed between the inner fitting portion 102 and the end portion of the coil spring 107. As a result, the rigidity of the spring seat rubber 1 in the direction perpendicular to the axis and in the axial direction can be increased. Since the rigidity of the spring seat rubber 1 in the direction perpendicular to the axis and in the axial direction when receiving a lateral force and an axial load (load corresponding to the vehicle's own weight) from the coil spring 107 can be increased, the steering stability of the vehicle is improved. be able to.

  The abutment surface 21 abuts on the flange portion 103 (continuous portion 104) in a state where the main body portion 10 is fitted to the internal fitting portion 102 of the mounting apparatus 100 and the spring seat rubber 1 is not subjected to the axial load. A contact portion 21a and a gap forming portion 21b that forms a gap G with the flange portion 103 are provided on the radially outer side of the contact portion 21a. In the gap forming portion 21b, the axial end surface on one end side in the axial direction (upper side in FIG. 1) is in the state where no load is applied in the axial direction, and the other end side in the axial direction from the axial end surface of the contact portion 21a (see FIG. 1 is formed so as to be located on the other end side in the axial direction (lower side in FIG. 1) as it goes radially outward from the contact portion 21a.

  In addition, the overhang | projection part 20 is formed so that the cross-sectional area orthogonal to the axial center O may increase as it goes below (FIG. 1 lower direction) in the site | part in which the clearance gap formation part 21b is formed. As a result, the mounting device 100 can obtain an appropriate spring constant by increasing the contact area between the projecting portion 20 and the flange portion 103 as the axial load input to the projecting portion 20 increases.

  Next, with reference to FIG.2 and FIG.3, the detailed structure of the spring seat rubber 1 is demonstrated. 2 is a perspective view of the spring seat rubber 1 (no load), and FIG. 3 is a plan view of the spring seat rubber 1 (no load). As shown in FIGS. 2 and 3, the spring seat rubber 1 has contact portions 21 a formed at equal intervals at six locations in the circumferential direction of the contact surface 21 (see FIG. 1). The contact portion 21a is formed in a substantially fan shape in plan view, and is located radially, and a gap forming portion 21b is formed on the radially outer side of the contact portion 21a. The gap forming portion 21b is formed on the outer side in the radial direction of the contact portion 21a and the groove 23 except for a portion where a recessed portion 25 (described later) is formed. The concave groove 23 is a part for adjusting the spring constant of the overhanging portion 20, and is formed radially between the contact portions 21 a of the contact surface 21.

  The main body 10 is provided with concave portions 24 that are radially outward at three locations in the circumferential direction of the inner periphery 10a at equal intervals. The concave portion 24 is a position of the cylindrical metal fitting 30 (cylindrical portion 31) embedded in the main body portion 10 from the radially inner end portion of the contact portion 21a toward the other end side in the axial direction (the back side in FIG. 3). It is extended to. Here, when the spring seat rubber 1 is attached to the mounting device 100, a space by the concave portion 24 is formed between the inner fitting portion 102 and the inner periphery 10 a of the main body portion 10. When an axial load is applied to the spring seat rubber 1, a part of the elastically deformed spring seat rubber 1 is accommodated in the space formed by the recess 24. Thereby, since the whole spring seat rubber 1 can be elastically deformed substantially uniformly, it can prevent that a big load acts on the spring seat rubber 1 locally. As a result, the durability of the spring seat rubber 1 can be improved.

  Here, with reference to FIG. 4, the mounting bracket 101 of the mounting device 100 to which the spring seat rubber 1 is fitted will be described. FIG. 4 is a bottom view of the mounting bracket 101 of the mounting apparatus 100. The mounting bracket 101 is a part of the mounting device 100 and includes an inner fitting portion 102 formed in a cylindrical shape and a flange portion 103 provided continuously to the radially outer side of the inner fitting portion 102. The outer diameter of the inner fitting portion 102 is larger than the inner diameters of the main body portion 10 and the overhanging portion 20 of the spring seat rubber 1 (the extent that the main body portion 10 and the overhanging portion 20 are elastically deformed and are fitted into the inner fitting portion 102). The outer diameter of the flange portion 103 is set to be larger than the outer diameter of the overhang portion 20 of the spring seat rubber 1.

  The flange portion 103 has three insertion holes 103a through which bolts (not shown) fastened to the vehicle body (not shown) are inserted. The insertion holes 103a are holes that penetrate in the thickness direction of the flange portion 103, and are formed at three equal intervals in the circumferential direction. In addition, the inner fitting portion 102 is provided with concave portions 102a that are directed radially inward at three locations in the circumferential direction of the outer periphery at equal intervals. The concave portion 102a is a portion formed in a concave groove shape along the axial direction of the inner fitting portion 102 (the vertical direction in FIG. 4).

  Returning to FIG. 3, the spring seat rubber 1 will be described. The spring seat rubber 1 has a recessed portion 25 formed at a position corresponding to the insertion hole 103a (see FIG. 4) of the mounting device 100 (mounting bracket 101). The recessed portion 25 is a portion in which the head of a bolt (not shown) inserted through the insertion hole 103a of the mounting apparatus 100 is accommodated, and three locations in the circumferential direction of the overhang portion 20 (the radial direction of the recessed groove 23). It is recessed on the outside. Since the recessed portion 25 is recessed in the radially outer side of the recessed groove 23 that adjusts the spring constant of the overhanging portion 20, the dynamic spring formed by the contact portion 21a and the gap forming portion 21b set in advance becomes the recessed portion. Fluctuation due to interference between the heads of bolts (not shown) accommodated in the recesses 25 and the recesses 25 can be prevented.

  The spring seat rubber 1 includes ridge-shaped convex portions 12 projecting from the inner periphery toward the axis O at three locations in the circumferential direction of the main body portion 10. The convex portion 12 is a portion that engages with a concave portion 102a provided in the inner fitting portion 102 of the mounting device 100 (mounting bracket 101), and extends along the axial direction of the main body portion 10 (perpendicular to the plane of FIG. 3). It is formed in a ridge shape. In the present embodiment, the convex portion 12 protrudes radially inward of the inner periphery 10a where the contact portion 21a is formed on the axial end surface.

  The protrusion 12 of the spring seat rubber 1 and the recess 102a of the mounting device 100 are made to coincide with each other, and the axis O of the spring seat rubber 1 is made to coincide with the extension of the axis O of the inner fitting portion 102, thereby making the spring seat rubber 1 Is moved from the inner fitting portion 102 toward the flange portion 103 side, the spring seat rubber 1 is externally fitted to the mounting device 100 (mounting bracket 101), and the contact surface 21a of the spring seat rubber 1 is moved to the flange portion 103 (continuous). Abuts against the mounting portion 104).

  At this time, since the convex portion 12 of the spring seat rubber 1 and the concave portion 102a of the mounting device 100 are engaged, the spring seat rubber 1 may move relative to the mounting device 100 (mounting bracket 101) in the circumferential direction. Is prevented. Further, since the convex portion 12 protrudes radially inward of the inner periphery 10 a where the contact portion 21 a is formed on the axial end surface of the main body portion 10, the pressure receiving surface 22 of the spring seat rubber 1 is separated from the coil spring 107. When the contact portion 21 is compressed and deformed in the axial direction in response to the axial load, the convex portion 12 is deformed so as to protrude inward in the radial direction. Thus, the engagement between the convex portion 12 of the spring seat rubber 1 and the concave portion 102a of the mounting device 100 when an axial load is input to the spring seat rubber 1 can be ensured and strengthened.

  Next, with reference to FIG.5 and FIG.6, the relationship between the mounting apparatus 100 (mounting metal fitting 101) and the spring seat rubber 1 is demonstrated. FIG. 5 is an axial sectional view of the spring seat rubber 1 (without load) attached to the mounting device 100, and FIG. 6 is an axial sectional view of the spring seat rubber 1 when receiving a load from the coil spring 107. is there. 5 and 6 show a cross section on one side centered on the axis O in order to simplify the drawings and facilitate understanding.

  As shown in FIG. 5, the spring seat rubber 1 has a contact surface when no load is received from the coil spring 107 while the main body 10 is fitted to the inner fitting portion 102 of the mounting device 100. 21 includes a contact portion 21 a that contacts the flange portion 103 of the mounting apparatus 100, and a gap forming portion 21 b that is located radially outside the contact portion 21 a and forms a gap G with the flange portion 103 of the mounting apparatus 100. ing.

  In the present embodiment, the abutting portion 21a abuts on the continuous portion 104 located on the radially inner side of the flange portion 103 when there is no load. Further, at the time of no load, the gap forming portion 21b is at least partially located on the radially outer side (left side in FIG. 5) of the virtual first cylinder C1 that extends the outer periphery 10b of the main body portion 10 in the axial direction. The axial thickness between the pressure receiving surface 22 and the contact surface 21 is set so as to decrease from the inner side in the direction toward the outer side in the radial direction. In addition, at the time of no load, the gap forming portion 21b is at least partially positioned on the radially outer side of the virtual substantially truncated cone-shaped second cylinder C2 extending in the axial direction from the cylindrical portion 31 of the cylindrical metal fitting 30. The thickness in the axial direction between the flange portion 32 of the cylindrical metal fitting 30 and the contact surface 21 is set so as to decrease from the radially inner side toward the radially outer side.

  As shown in FIG. 6, a coil spring 107 is fitted to the outer periphery 10b of the main body 10 to constitute a suspension mechanism in a vehicle (not shown). When a vehicle (not shown) is grounded, an axial load is input to the suspension mechanism by the weight of the vehicle. As a result, the end of the coil spring 107 fitted on the shock absorber (not shown) moves to one end side in the axial direction (upward in FIG. 6). Then, the pressure receiving surface 22 of the spring seat rubber 1 receives an axial load from the coil spring 107, and the contact surface 21 facing the pressure receiving surface 22 is elastically deformed. Since the main body portion 10 is fitted into the inner fitting portion 102 of the mounting apparatus 100, the elastic deformation of the contact surface 21 in the radially inner direction is restricted by the inner fitting portion 102. Therefore, the contact surface 21 is elastically deformed outward in the axial direction and the radial direction.

  When the axial load is not input to the spring seat rubber 1 (see FIG. 5), there is a gap G between the gap forming portion 21b and the flange portion 103 located on the radially outer side of the contact portion 21a. Therefore, when receiving an axial load, the gap forming portion 21b is displaced in the axial direction more than the contact portion 21a. As a result, since the amount of elastic deformation of the gap forming portion 21b toward the radially outer side can be reduced, the overhanging portion 20 can hardly be spread radially outward.

  Here, when the overhanging portion 20 spreads radially outward and rides on the flange portion 103 of the mounting apparatus 100, the edge of the flange portion 103 comes into contact with the overhanging portion 20 and the overhanging portion 20 is easily damaged. If it does so, there exists a possibility that durability of the spring seat rubber 1 may fall. Further, when the overhanging portion 20 is elastically deformed and spreads outward in the radial direction, the rubber volume of the overhanging portion 20 interposed between the flange portion 103 of the mounting device 100 and the end of the coil spring 107 becomes small. . If it does so, there exists a possibility that the rigidity of the spring seat rubber 1 (overhang | projection part 20) may become large, and the damping performance by the spring seat rubber 1 may fall.

  On the other hand, according to the present embodiment, the gap forming portion 21b can reduce the amount of elastic deformation of the overhanging portion 20 radially outward, so that the gap forming portion 21b (the overhanging portion) is formed on the flange portion 103 of the mounting device 100. 20) can be made difficult. As a result, it can suppress that the overhang | projection part 20 contacts the edge of the flange part 103. FIG. Therefore, the durability of the spring seat rubber 1 can be improved. Further, since the amount of elastic deformation of the gap forming portion 21b toward the outside in the radial direction can be reduced, the rubber volume of the overhang portion 20 interposed between the flange portion 103 of the mounting device 100 and the end portion of the coil spring 107 can be reduced. It can be secured. Therefore, the vibration damping performance of the spring seat rubber 1 can be ensured.

  Further, in the spring seat rubber 1, when no load is applied, at least a part of the gap forming portion 21b is located on the radially outer side of the virtual first cylinder C1 that extends the outer periphery 10b of the main body portion 10 in the axial direction. When the pressure-receiving surface 22 receives an axial load from the coil spring 107 whose end is disposed on the outer periphery 10b of the main body 10, the gap forming portion 21b positioned radially outside the virtual first cylinder C1 is elastic in the axial direction. Deform. As a result, the rubber volume of the overhanging portion 20 interposed between the flange portion 103 of the mounting device 100 and the end portion of the coil spring 107 can be secured. Therefore, an increase in rigidity of the spring seat rubber 1 (the overhang portion 20) interposed between the flange portion 103 and the coil spring 107 can be suppressed. As a result, the vibration damping performance of the spring seat rubber 1 can be improved.

  In particular, in the present embodiment, since the contact portion 21a is positioned on the virtual first cylinder C1, all of the gap forming portions 21b can be positioned on the radially outer side of the first cylinder C1. As a result, due to the axial load input by the end of the coil spring 107, all of the gap forming portion 21b is displaced in the axial direction. Thereby, an increase in the rigidity of the gap forming part 21b can be suppressed while ensuring the rigidity of the contact part 21a. As a result, the vibration control performance can be improved by the gap forming portion 21b while ensuring the steering stability of the vehicle by the contact portion 21a.

  Here, the gap forming portion 21b is configured such that, when there is no load, the axial thickness of the overhang portion 20 between the pressure receiving surface 22 and the contact surface 21 decreases from the radially inner side toward the radially outer side. Is set. Therefore, when the pressure receiving surface 22 receives an axial load from the coil spring 107, the rubber volume of the overhang portion 20 that expands radially outward can be reduced. As a result, it is possible to make it difficult for the overhanging portion 20 to ride on the flange portion 103 of the mounting apparatus 100, so that the durability of the spring seat rubber 1 can be improved.

  The overhang portion 20 of the spring seat rubber 1 is set to have a smaller outer diameter than the outer diameter of the flange portion 103 when there is no load. Thereby, even if the overhang | projection part 20 is elastically deformed to radial direction outer side and diameter-expanded, it can be made hard to make the edge of the flange part 103 and the overhang | projection part 20 interfere. As a result, it is possible to prevent the overhanging portion 20 from being cracked or damaged by the edge of the flange portion 103. Therefore, the durability of the spring seat rubber 1 can be improved.

  Further, according to the present embodiment, the cylindrical portion 31 of the cylindrical metal fitting 30 is embedded in the other end side (the lower side in FIG. 5) of the main body portion 10 in the axial direction. Therefore, when the pressure receiving surface 22 receives an axial load from the coil spring 107, the contact surface 21 is elastically deformed radially inward by the inner fitting portion 102 of the mounting device 100 and the cylindrical portion 31 of the cylindrical metal fitting 30. Is limited. In addition, the cylindrical portion 31 embedded in the main body 10 can increase the rigidity of the main body 10 in the direction perpendicular to the axis (the left-right direction in FIG. 5) to improve the steering stability of the vehicle.

  In addition, at the time of no load, the clearance gap formation part 21b is located in the radial direction outer side (FIG. 5 left side) of the virtual 2nd cylinder C2 which extended the cylindrical part 31 of the cylindrical metal fitting 30 to the axial direction. Therefore, when the pressure receiving surface 22 receives an axial load from the coil spring 107, the gap forming portion 21b is elastically deformed outward in the axial direction and in the radial direction. Since the gap forming portion 21b has a gap with the flange portion 103, the amount of elastic deformation of the gap forming portion 21b outward in the radial direction can be reduced by deforming the gap forming portion 21b in the axial direction more than the contact portion 21a. . As a result, it is possible to make it difficult to ride the gap forming portion 21b on the flange portion 103 of the mounting apparatus 100. Therefore, durability of the spring seat rubber 1 in which the cylindrical portion 31 is embedded in the main body portion 10 can be improved.

  In this case, since the amount of elastic deformation of the gap forming portion 21b toward the radially outer side can be reduced, the rubber volume of the overhanging portion 20 interposed between the flange portion 103 of the mounting device 100 and the end portion of the coil spring 107. Can be secured. Therefore, it is possible to ensure the vibration damping performance of the spring seat rubber 1 (the overhang portion 20) in which the cylindrical portion 31 is embedded in the main body portion 10.

  In particular, in the present embodiment, since the contact portion 21a is positioned on the virtual second cylinder C2, all the gap forming portions 21b can be positioned on the radially outer side of the second cylinder C2. Although the displacement of the main body portion 10 is restricted to some extent by the cylindrical portion 31, all of the gap forming portion 21 b is displaced in the axial direction by the axial load input by the end portion of the coil spring 107. Thereby, an increase in the rigidity of the gap forming part 21b can be suppressed while ensuring the rigidity of the contact part 21a. As a result, the vibration control performance can be improved by the gap forming portion 21b while ensuring the steering stability of the vehicle by the contact portion 21a.

  Furthermore, according to the present embodiment, the flange portion 32 that bulges outward in the radial direction from one axial end side of the cylindrical portion 31 is embedded in the overhang portion 20. Since the gap forming portion 21b is set to have a smaller thickness in the axial direction of the overhanging portion 20 between the flange portion 32 and the contact surface 21 from the radially inner side to the radially outer side when no load is applied, When the flange portion 32 receives an axial load from the coil spring 107 via the pressure receiving surface 22, the gap forming portion 21b can be hardly spread outward in the radial direction. As a result, it is possible to make it difficult for the overhanging portion 20 to ride on the flange portion 103 of the mounting apparatus 100, so that the durability of the spring seat rubber 1 can be further improved.

  In particular, in the present embodiment, the outer periphery 20a of the overhanging portion 20 and the gap forming portion 21b intersect with the flange 32 embedded in the overhanging portion 20 at one end side in the axial direction (upper side in FIG. 5). A rubber volume of the overhang portion 20 interposed between the flange portion 103 of the mounting device 100 and the radially outer side of the flange portion 32 can be secured. Therefore, the vibration damping performance of the spring seat rubber 1 in which the flange portion 32 is embedded in the overhang portion 20 can be ensured.

  Further, in the present embodiment, the mounting device 100 (mounting bracket 101) has a continuous portion 104 that is inserted into the inner fitting portion 102 side on the radially inner side of the flange portion 103. The abutting portion 21a comes into contact with the butt. Since the gap G between the flange portion 103 and the gap forming portion 21b can be increased by the amount of the continuous portion 104, compared to a flat surface-like flange portion in which the continuous portion 104 is not formed, the shaft of the gap forming portion 21b The amount of displacement in the direction can be increased. As a result, it is possible to suppress the amount of diameter expansion of the overhanging portion 20 to the outside in the radial direction when an axial load is input, and to prevent the rigidity of the overhanging portion 20 from becoming excessive.

  Next, a second embodiment will be described with reference to FIG. In the first embodiment, the spring seat rubber 1 in which the cylindrical metal fitting 30 is embedded has been described. On the other hand, 2nd Embodiment demonstrates the spring seat rubber 41 in which the cylindrical metal fitting is not embed | buried. Since the spring seat rubber 41 in the second embodiment is the same as that in the first embodiment except that the cylindrical metal fitting is not embedded, the same parts as those explained in the first embodiment are the same. The following description is omitted. FIG. 7 is an axial sectional view of a spring seat rubber 41 (no load) in the second embodiment. In FIG. 7, in order to simplify the drawing and facilitate understanding, a cross section on one side centered on the axis O is shown (the same applies in FIG. 8).

  According to the spring seat rubber 41 shown in FIG. 7, at the time of no load, the gap forming portion 21b is at least partly radially outward of the virtual first cylinder C1 that extends the outer periphery 10b of the main body portion 10 in the axial direction. Located in. Further, the gap forming portion 21b is configured such that, when there is no load, the axial thickness of the overhang portion 20 between the pressure receiving surface 22 and the contact surface 21 decreases from the radially inner side toward the radially outer side. Is set. Therefore, the same operations and effects as those of the first embodiment can be realized.

  Next, a third embodiment will be described with reference to FIG. In 1st Embodiment, the spring seat rubber 1 with which the cylindrical metal fitting 30 provided with the cylindrical part 31 and the collar part 32 was embed | buried was demonstrated. On the other hand, in 3rd Embodiment, the spring seat rubber 51 by which the cylindrical metal fitting 60 (cylindrical part) by which the collar part was abbreviate | omitted is embed | buried under the main-body part 10 is demonstrated. In addition, about the part same as the part demonstrated in 1st Embodiment, the same code | symbol is attached | subjected and the following description is abbreviate | omitted. FIG. 8 is an axial sectional view of the spring seat rubber 51 in the third embodiment.

  The spring seat rubber 51 is a member for reducing vibrations transmitted from the wheel (not shown) side to the vehicle body (not shown) side via the coil spring 107 and has a substantially cylindrical shape having an axis O. A main body portion 10 formed, and a projecting portion 52 formed in a substantially annular shape by projecting from the one end side in the axial direction of the main body portion 10 (upper end portion in FIG. 8) to the outer side in the axial direction. Yes. The overhang portion 52 is configured as a contact surface 53 configured as a surface coupled to the inner periphery 10 a of the main body 10 and a flat surface opposed to the contact surface 53 and coupled to the main body 10. The pressure receiving surface 55 is provided.

  The main body 10 is embedded with a cylindrical metal fitting 60 formed in a cylindrical shape from a metal material. The cylindrical metal fitting 60 has an axial length that is the length of the main body 10 excluding the overhang 52 (the length from the pressure receiving surface 55 to the axial end of the main body 10 (the lower end in FIG. 8)). )).

  The abutment surface 53 abuts on the flange portion 103 (continuous portion 104) in a state where the main body portion 10 is fitted to the internal fitting portion 102 of the mounting apparatus 100 and the spring seat rubber 51 is not subjected to the axial load. A contact portion 21a and a gap forming portion 54 that forms a gap G with the flange portion 103 are provided on the radially outer side of the contact portion 21a. The gap forming portion 54 is in a state in which no load is applied in the axial direction, and the axial end surface on one end side in the axial direction (upper side in FIG. 8) is the other end side in the axial direction from the axial end surface in the contact portion 21a. 8 (lower side) and is curved toward the other end side (lower side in FIG. 1) in the axial direction as it goes radially outward from the contact portion 21a (convex toward the flange portion 103). The curved surface).

  The overhanging portion 52 is formed such that the cross-sectional area perpendicular to the axis O is increased downward (downward in FIG. 8) at the portion where the gap forming portion 54 is formed. As a result, the mounting device 100 can obtain an appropriate spring constant by increasing the contact area between the protruding portion 52 and the flange portion 103 as the axial load input to the protruding portion 52 increases.

  When no load is applied, at least a part of the gap forming portion 54 is located on the radially outer side (the left side in FIG. 8) of the virtual first cylinder C1 extending in the axial direction from the outer periphery 10b of the main body portion 10, and is radially inward. Is set so that the axial thickness of the overhanging portion 52 between the pressure receiving surface 55 and the contact surface 53 becomes smaller toward the outer side in the radial direction. In addition, at the time of no load, the gap forming part 54 is at least partially positioned on the radially outer side of the virtual second cylinder C2 obtained by extending the cylindrical metal fitting 60 in the axial direction. In the present embodiment, the gap forming portion 54 and the contact portion 21a are located on the radially outer side of the second cylinder C2 when there is no load.

  Also in the spring seat rubber 51, the gap forming portion 54 can realize the same operations and effects as in the first embodiment. In particular, the spring seat rubber 51 has the gap forming portion 54 and the abutting portion 21a located outside in the radial direction of the second cylinder C2 when no load is applied, so that the gap forming portion 54 when the axial load is input is provided. It is possible to prevent the dynamic spring from becoming excessive, and to secure the vibration control performance.

  The present invention has been described above based on the embodiments. However, the present invention is not limited to the above embodiments, and various improvements and modifications can be made without departing from the spirit of the present invention. It can be easily guessed. For example, the numbers and shapes of the contact portions 21a and the concave grooves 23 and the shapes and dimensions of the gap forming portions 21b and 54 mentioned in the above embodiment are merely examples, and other shapes and numerical values can naturally be adopted. is there.

  In each of the above-described embodiments, the case where the concave grooves 23 for adjusting the spring constants of the spring seat rubbers 1, 41, 51 are formed radially on the contact surfaces 21, 53 has been described. As a result, the contact portion 21a was divided in the circumferential direction by the concave groove 23. However, the present invention is not necessarily limited to this. The spring constant of the spring seat rubber is adjusted by selecting an appropriate rubber-like elastic body, and the abutting portion 21a is continuously provided in the circumferential direction by omitting the concave groove. It is naturally possible to form. Thereby, the elastic deformation in the axial direction of the spring seat rubber can be made substantially uniform in the circumferential direction, and a large load can be prevented from acting on the spring seat rubber locally. As a result, the durability of the spring seat rubber can be improved.

  In each of the above-described embodiments, the concave grooves 23 are formed radially on the contact surfaces 21 and 53, and the gap forming portions 21b and 54 except for the portion where the concave portions 25 are formed, The case where it forms in the radial direction outer side of 23 was demonstrated. However, the present invention is not necessarily limited to this, and when the axial depth of the concave groove 23 is relatively large with respect to the inclination of the gap forming portions 21b and 54, the gap forming portion is formed radially outward of the concave groove 23. Of course, it is possible to prevent 21b and 54 from being formed. Also in this case, as in the present embodiment, the spring constant is adjusted by the concave groove 23, and the protrusions 20 and 53 can be prevented from climbing onto the flange portion 103 by the gap forming portions 21b and 54.

  In each of the above embodiments, the case where the continuous portion 104 is formed in the flange portion 103 of the mounting apparatus 100 has been described. However, the present invention is not limited to this, and the flange portion 103 is omitted by omitting the continuous portion 104. It is naturally possible to make it flat (flat surface). In this case as well, since there are gap forming portions 21b and 54 as in the present embodiment, it is possible to prevent the overhang portions 20 and 53 from riding on the flange portion 103.

  In each of the above embodiments, when there is no load, the virtual first cylinder C1 that extends the outer periphery 10b of the main body 10 in the axial direction, and the cylindrical portion 31 and the cylindrical fitting 60 (cylindrical portion) are extended in the axial direction. The case where all of the gap forming portions 21b and 54 are located outside in the radial direction of the virtual second cylinder C2 has been described. However, it is not necessarily limited to this. If at least a part of the gap forming portions 21b and 54 is set so as to be positioned on the radially outer side of the first cylinder C1 and the second cylinder C2, the protruding portions 20 and 53 when an axial load is input are set. This is because the amount of elastic deformation outward in the radial direction can be suppressed, so that the same actions and effects as in the above embodiments can be realized.

1, 41, 51 Spring seat rubber 10 Main body portion 10b Outer periphery 20, 52 Overhang portion 21, 53 Contact surface 21a Contact portion 21b, 54 Gap formation portion 22, 55 Pressure receiving surface 23 Concave groove 24 Concave portion 30 Cylindrical metal fitting 31 Cylindrical part 32 collar part 60 cylindrical fitting (cylindrical part)
DESCRIPTION OF SYMBOLS 100 Mount apparatus 102 Internal fitting part 103 Flange part 107 Coil spring C1 1st cylinder C2 2nd cylinder

Claims (5)

A spring seat comprising a mounting device having a flange portion provided continuously with a cylindrical inner fitting portion, and a rubber-like elastic body interposed between the flange portion of the mounting device and an end portion of a coil spring. In a suspension mechanism comprising a rubber,
The spring seat rubber has an annular main body portion as viewed in the axial direction;
A projecting portion formed by projecting radially outward from the outer peripheral side on one end side in the axial direction of the main body portion;
The main body portion and the overhanging portion are located on one end side in the axial direction and are in contact with the flange portion, and are located on the other end side in the axial direction and face the contact surface, and A pressure receiving surface for receiving the end,
The abutment surface includes an abutment portion that abuts against the flange portion when the main body portion is fitted to the internal fitting portion and no load is applied to the coil spring, and the contact portion is in contact with the flange portion. A gap forming portion that is located radially outside the contact portion and forms a gap with the flange portion;
The flange portion includes a continuous portion with which the abutting portion abuts,
The suspension mechanism according to claim 1, wherein the continuous portion is located on the other end side in the axial direction with respect to the flange portion where the gap forming portion abuts when receiving an axial load from the coil spring.   2. The gap forming portion according to claim 1, wherein at least a part of the gap forming portion is located on a radially outer side of a virtual first cylinder in which an outer periphery of the main body portion is extended in the axial direction at the time of no load. Suspension mechanism. The main body is provided with a recess from the radially inner end of the contact portion toward the other end in the axial direction.
3. The suspension mechanism according to claim 1, wherein a portion of the gap forming portion located radially outside the concave portion is continuous with a portion located on both sides in the circumferential direction of the portion . A plurality of concave grooves that are recessed toward the other end side in the axial direction are formed in the contact surface over the entire length in the radial direction,
The suspension mechanism according to claim 3, wherein the concave portion is disposed between the plurality of concave grooves. A cylindrical portion formed in a cylindrical shape, and a flange portion that protrudes radially outward from one end side in the axial direction of the cylindrical portion and is formed in a bowl shape, and on the other end side in the axial direction of the main body portion It is equipped with a cylindrical fitting that is buried,
The thickness of the main body portion and the overhang portion between the flange portion and the pressure receiving surface is set larger than the thickness of the main body portion on the pressure receiving surface side with respect to the cylindrical portion. The suspension mechanism according to any one of claims 1 to 4.

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