Support structure for coil spring in vehicular suspension mechanism

Abstract

This support structure for a coil spring (1) in a vehicular suspension mechanism includes: the coil spring (1); and a spring receiver (15) that receives one end of the coil spring (1) in the axial direction. The spring receiver (15) has a contact part (16) that comes into contact with one end of the coil spring (1) when the vehicle is unloaded and stopped, the contact part extending along the circumferential direction of the coil spring. The contact part (16), other than both end sections in the circumferential direction of the contact part (16), is provided with a high resilience section (14). The high resilience section (14) has a higher rigidity than any part of the contact part (16) that is not the high resilience section (14).

Description

Coil spring support structure for vehicle suspension mechanism

[0001] The present invention relates to a support structure for a coil spring of a vehicle suspension mechanism.

[0002] In a vehicle suspension mechanism, suspension springs are used to absorb shocks input from the road surface to the vehicle as the vehicle travels. In addition to absorbing shocks during travel, suspension springs also serve to support the vehicle body and control the vehicle body's attitude relative to the road surface. Leaf springs and coil springs are used as suspension springs. In the case of a coil spring, the upper end is typically mounted to the vehicle body, and the lower end is mounted to a suspension member that moves up and down relative to the vehicle body. Patent Document 1 discloses related technology.

[0003] JP 2008-248949 A

[0004] So-called open-end coil springs, in which the wire ends do not contact each other, have an end turn portion. A spring retainer that receives one axial end of the coil spring contacts the end turn portion at a contact portion that extends along the circumferential direction of the coil spring. The load input from the coil spring to the spring retainer tends to concentrate at the circumferential end of the contact portion. As a result, the center of the load input to the spring retainer may be significantly offset from the central axis of the coil spring.

[0005] SUMMARY OF THE INVENTION An object of the present invention is to prevent an excessively biased load from acting on a spring receiver in a support structure for a coil spring of a vehicle suspension mechanism.

[0006] A coil spring support structure for a vehicle suspension mechanism according to one aspect of the present invention includes a coil spring and a spring bearing that receives one axial end of the coil spring. The spring bearing has a contact portion that extends circumferentially of the coil spring and that contacts one end of the coil spring when the vehicle is parked empty. A high reaction force portion is provided in the contact portion other than both circumferential ends of the contact portion, and the high reaction force portion has higher rigidity than the other portions of the contact portion.

[0007] The above-described support structure for the coil spring can prevent an excessively unbalanced load from acting on the spring receiver.

[0008] FIG. 1 is a cross-sectional view of the support structure for a coil spring according to the first embodiment (cross-sectional view taken along line II in FIG. 2). FIG. 2 is a bottom view of the spring receiver in the support structure of FIG. 1. FIG. 3 is an exploded perspective view showing the spring receiver and a coil spring. FIG. 4 is a perspective view of the spring receiver as seen from below. FIG. 5 is an exploded perspective view of the spring receiver as seen from below. FIG. 6 is a cross-sectional view of the spring receiver and the upper end of the coil spring (cross-sectional view taken along line VI-VI in FIG. 2). FIG. 7 is a cross-sectional view showing a modified example of the first embodiment. FIG. 8 is a perspective view of the spring receiver of the support structure for a coil spring according to the second embodiment as seen from below. FIG. 9 is an exploded perspective view of the spring receiver of FIG. 8 as seen from below. FIG. 10 is a cross-sectional view showing a modified example of the second embodiment.

[0009] Hereinafter, with reference to the drawings, a coil spring support structure for a vehicle suspension mechanism according to an embodiment will be described, taking as an example a case where it is applied to an upper mount of a strut-type suspension for steered wheels.

[0010] <First Embodiment> As shown in Figure 1, a suspension mechanism according to the first embodiment includes a coil spring 1 and a strut, i.e., a shock absorber 2, disposed inside the coil spring 1. The coil spring 1 not only absorbs shocks input from the road surface to the vehicle body while the vehicle is traveling, but also supports the vehicle body and controls the attitude of the vehicle body relative to the road surface. The shock absorber 2, also known as a damper, absorbs vibrations caused by the expansion and contraction of the coil spring 1. The shock absorber 2 includes a piston rod 3 that protrudes upward from a cylinder (not shown).

[0011] As shown in Figure 1, the upper end of the piston rod 3 of the shock absorber 2 and the upper end of the coil spring 1 are mounted to a vehicle body 4, specifically, a suspension tower in the engine room or motor room. In this upper mount, a metal mount plate 5, for example, is fixed to the suspension tower with bolts and nuts, and the piston rod 3 and coil spring 1 are mounted to the vehicle body 4 via the mount plate 5. A recess 6 is formed in the center of the mount plate 5, and an insertion hole 60 is formed in the center of the recess 6, through which the upper end of the piston rod 3 is inserted. A top insulator 7, on which the piston rod 3 of the shock absorber 2 is mounted, is rotatably housed inside the recess 6.

[0012] The top insulator 7 is composed of a ring 70, an annular outer bush 71, an annular inner bush 72, and a circular plate 73. The outer bush 71 is fixed inside the ring 70. The inner bush 72 is embedded integrally inside the outer bush 71. The plate 73 is embedded in the inner bush 72. The ring 70 and the plate 73 are made of, for example, metal, and the outer bush 71 is made of rubber. The inner bush 72 is made of, for example, rubber or resin, and has higher rigidity than the outer bush 71. The top insulator 7 is rotatably housed in the recess 6 while being sandwiched between the mount plate 5 and the vehicle body 4. A fixing hole 74 is formed in the center of the plate 73, through which the upper end of the piston rod 3 is inserted. The upper end of the piston rod 3 is fastened and fixed to the fixing hole 74 of the plate 73 by a nut 8. A load input from the piston rod 3 to the vehicle body 4 is input to the vehicle body 4 via the top insulator 7.

[0013] An annular upper bearing case 9U is fitted around the recess 6 on the underside of the mount plate 5. The upper bearing case 9U is paired with an annular lower bearing case 9L provided below it to form the bearing case 9. The bearing case 9 is made of, for example, hard resin.

[0014] An annular thrust bearing 10 is housed between the upper bearing case 9U and the lower bearing case 9L. An annular spring insulator 11 is attached to the underside of the lower bearing case 9L. Hereinafter, the spring insulator 11 will also be simply referred to as the insulator 11.

[0015] 4 and 5 , the insulator 11 has a general portion 12 and a high-rigidity portion 13. The high-rigidity portion 13 is formed integrally with the general portion 12 and has higher rigidity than the general portion 12. In this embodiment, the portion of the insulator 11 other than the high-rigidity portion 13 is composed of the general portion 12, and the high-rigidity portion 13 is molded integrally with the general portion 12 so as to be embedded within the insulator 11.

[0016] The general portion 12 is made of, for example, rubber. A typical material for the general portion 12 is an elastomer (PP+EPDM) made of polypropylene and ethylene propylene diene rubber, and its Young's modulus is approximately 120 MPa. The high-rigidity portion 13 is made of, for example, a hard resin. A typical material for the high-rigidity portion 13 is polypropylene PP-G30 containing 30% glass fiber by weight, and its Young's modulus is approximately 4000 MPa. The material for the high-rigidity portion 13 is not particularly limited, and may be metal, etc.

[0017] The lower bearing case 9L and the insulator 11 constitute a spring support 15 that supports one axial end of the coil spring 1. The lower bearing case 9L is an insulator support member that is provided on the opposite side of the insulator 11 from the coil spring 1 and comes into contact with the insulator 11.

[0018] The upper mount of this embodiment is a so-called separated-input mount, and as shown in FIG. 1 , the load input path from the shock absorber 2 to the vehicle body 4 is separated from the load input path from the coil spring 1 to the vehicle body 4. In this separated-input mount, by softening the outer bushing 71 of the top insulator 7 located on the load input path from the shock absorber 2, it is possible to suppress the transmission of high-frequency micro-vibration input that is a source of road noise and the like. On the other hand, by stiffening the insulator 11 of the spring bearing 15 located on the load input path from the coil spring 1, it is possible to stably receive the large load input from the coil spring 1. As a result, it is possible to achieve improved ride comfort and reduced road noise while ensuring the strength, durability, and handling stability of the upper mount.

[0019] Although not shown in the drawings, the cylinder of the shock absorber 2 is provided with a lower spring bearing that receives the axial lower end of the coil spring 1. The lower spring bearing is composed of, for example, a metal circular plate-shaped flange welded to the metal cylinder, and a rubber insulator interposed between this flange and the lower end of the coil spring 1.

[0020] As shown in FIG. 1 , the coil spring 1 is a so-called open-end coil spring in which the wire ends do not contact each other. One axial end of the coil spring 1 has a C-shaped end turn portion 1B that contacts a spring retainer 15. The spring retainer 15 contacts the end turn portion 1B at a contact portion 16. As shown by the dotted hatching in FIG. 2 , the contact portion 16 forms a C-shape extending along the circumferential direction CD of the coil spring 1. Note that FIG. 1 shows the vehicle in an empty-vehicle stopped state. In this state, the coil spring 1 supports the sprung weight of the vehicle and is in a compressed state. The empty-vehicle stopped state refers to a state in which the vehicle is stopped on a level road surface and the empty weight is applied to the suspension mechanism. The empty weight is the empty vehicle mass defined in Japanese Industrial Standard JIS D 0102. FIG. 2 is a bottom view of the spring retainer 15 as viewed from the axial direction of the coil spring 1. In FIG. 2 , the coil spring 1 is indicated by a dashed line.

[0021] As shown in Figures 2 and 3, one circumferential end of the contact portion 16 contacts one end of the end winding portion 1B of the coil spring 1, i.e., the starting end 1S of the spiral. The other circumferential end of the contact portion 16 contacts the other end of the end winding portion 1B of the coil spring 1. The other end of the end winding portion 1B is connected to the coil body portion 1A of the coil spring 1. The coil body portion 1A is the portion of the coil spring 1 that is away from the spring receiver 15 (insulator 11) and functions as a spring. Hereinafter, the other end of the end winding portion 1B will be referred to as the contact end 1E of the coil spring 1. That is, one circumferential end of the contact portion 16 is the portion that contacts the starting end 1S of the end winding portion 1B, and the other is the portion that contacts the contact end 1E.

[0022] As shown in Figure 2, the contact portion 16 extends in an arc shape in the circumferential direction CD over an angle range of 216° to 270°. The angle θ3 of the contact end 1E is located within the angle range of 216° to 270° (216°≦θ3<270°). Here, the angle coordinates are defined with a point on the central axis O of the coil spring 1 as the origin. Furthermore, the angle θ is defined to take a positive value in the spiral winding direction of the coil spring 1 (counterclockwise in Figure 2) from the starting line (0° line) that passes through the origin and the tip of the starting end 1S when viewed in the axial direction of the coil spring 1.

[0023] As shown in Figures 4 and 5, the spring receiver 15 is provided with a high reaction force portion 14. As shown in Figure 2, the high reaction force portion 14 is provided in a portion of the contact portion 16 other than both circumferential ends of the contact portion 16. More specifically, the high reaction force portion 14 is parallel to a line segment LS connecting the circumferential ends of the contact portion 16 and is provided on the opposite side of a straight line L intersecting the central axis O of the coil spring 1 from the side on which the line segment LS is located. The high reaction force portion 14 has higher rigidity than the portions of the contact portion 16 other than the high reaction force portion 14.

[0024] In this embodiment, the axial reaction force per unit circumferential length of the high reaction force portion 14 is greater than the average value of the axial reaction force per unit circumferential length at the contact portion 16 on the opposite side of the line L from the side where the line segment LS is located (the region on the upper left side of the line L in FIG. 2 , with the line L as the boundary). The circumferential length is the length along the circumferential direction CD of the coil spring 1. The axial reaction force is the axial component of the reaction force input from the contact portion 16 to the seat turn portion 1B of the coil spring 1, i.e., the component parallel to the central axis O of the coil spring 1.

[0025] The circumferential end of the contact portion 16 is made up of a general portion 12, and the high reaction force portion 14 of the contact portion 16 has a high rigidity portion 13. Since the high rigidity portion 13 is embedded in the high reaction force portion 14, the crush allowance of the insulator 11 is relatively small. Therefore, the axial reaction force per unit circumferential length in the high reaction force portion 14 is larger than when the high rigidity portion 13 is not provided.

[0026] As shown in FIG. 2, the longitudinal center points of the high reaction force portion 14 and the high rigidity portion 13, i.e., the circumferential center point CP, are located within an angle range of 108° to 135°. In this embodiment, the angle θ1 of the end portion of the high reaction force portion 14 on the starting end 1S side is 108° or more, and the angle θ2 of the end portion of the high reaction force portion 14 on the contact end 1E side is 135° or less (108°≦θ1<θ2≦135°). The circumferential length of the high reaction force portion 14 is not particularly limited. The high reaction force portion 14 may extend over an angle range of, for example, 5° to 27°.

[0027] As shown in FIG. 5, the high-rigidity portion 13 also has an inclined surface 13S. The inclined surface 13S extends from a position radially inward of the coil spring 1 relative to an outer peripheral edge 16E (see FIG. 2) of the contact portion 16 to a position radially outward relative to the outer peripheral edge 16E, and is inclined toward the axial coil spring 1 as it extends radially outward. The inclination angle α of the inclined surface 13S relative to a reference plane P perpendicular to the axial direction of the coil spring 1 is 45° (see FIG. 6). Note that the inclination angle α of the inclined surface 13S relative to the reference plane P is measured on the acute angle side, not the obtuse angle side. That is, the inclination angle α is a positive value of 90° or less (0°<α≦90°).

[0028] The effects of the support structure for the coil spring 1 according to the first embodiment will be described.

[0029] (1) The load input from the open-end coil spring 1 to the spring receiver 15 tends to concentrate at the circumferential ends of the contact portion 16 (the portions corresponding to the contact start end 1S and the contact end 1E). Therefore, the center position of the load tends to be significantly shifted toward the circumferential ends from the central axis O of the coil spring 1.

[0030] In the support structure described above, the spring receiver 15 has a contact portion 16, as shown by dotted hatching in Fig. 2, when the vehicle is stopped empty. A high reaction force portion 14 is provided in the contact portion 16 in a portion other than both circumferential ends of the contact portion 16, and the high reaction force portion 14 has higher rigidity than the portion of the contact portion 16 other than the high reaction force portion 14.

[0031] Therefore, with the above support structure, the axial reaction force can be increased at the contact portions 16 other than at both circumferential ends. This allows the center of the load input to the spring bearing 15 to be closer to the central axis O of the coil spring 1, preventing excessively unbalanced loads from acting on the spring bearing 15. In particular, in this embodiment, the contact portions 16 have the high reaction force portions 14 on the opposite side of a line L, which intersects with the central axis O of the coil spring 1 and is parallel to a line LS connecting the circumferential ends of the contact portions 16, from the side where the line L is located, when viewed in the axial direction of the coil spring 1. This allows the axial reaction force to be increased at the contact portions 16 on the opposite side of the line L from the circumferential ends, thereby allowing the center of the load input to the spring bearing 15 to be closer to the central axis O of the coil spring 1. The position of the load center is equal to the position of the center of gravity of the distributed load input to the entire contact portion 16.

[0032] Furthermore, when the thrust bearing 10 is provided between the spring bearing 15 and the vehicle body 4 as in the above embodiment, an unbalanced load is prevented from being applied to the thrust bearing 10. This improves the life of the thrust bearing 10 and suppresses the generation of abnormal noise in the thrust bearing 10. In this way, the above support structure can be suitably applied to a strut-type suspension for steered wheels.

[0033] (2) In the above support structure, the spring bearing 15 includes an insulator 11 and a lower bearing case 9L that serves as an insulator bearing member, and the insulator 11 constitutes the high reaction force portion 14. Therefore, by adjusting the circumferential direction CD position of the insulator 11, the center of the load input to the spring bearing 15 can be easily moved closer to the central axis O of the coil spring 1. The insulator 11 also includes a general portion 12 and a high-rigidity portion 13 that has higher rigidity than the general portion 12. The circumferential end of the contact portion 16 is formed from the general portion 12. The high reaction force portion 14 of the contact portion 16 includes the high-rigidity portion 13. Therefore, with the above support structure, the distribution of the axial reaction force in the circumferential direction CD can be adjusted with a simple configuration, and the center of the load input to the spring bearing 15 can be moved closer to the central axis O of the coil spring 1.

[0034] (3) Figure 6 is a cross-sectional view taken along line VI-VI in Figure 2, with the right side showing a cross section at the starting end 1S and the left side showing a cross section at the high reaction force portion 14. In Figure 6, arrow B indicates a load input from the starting end 1S of the end winding portion 1B of the coil spring 1 to the general portion 12 of the insulator 11. Arrow C indicates a load input to the insulator 11 from a portion other than the starting end 1S and the contact end 1E of the end winding portion 1B when the high-rigidity portion 13 is not provided (when the entire insulator 11 is composed only of the general portion 12). Although not shown, the load input from the contact end 1E of the end winding portion 1B to the general portion 12 of the insulator 11 is equivalent to the load indicated by arrow B. Because the load input from the end winding portion 1B to the insulator 11 tends to concentrate at the starting end 1S and the contact end 1E, the load indicated by arrow B is greater than the load indicated by arrow C.

[0035] In the support structure described above, the high-rigidity portion 13 has an inclined surface 13S. The inclined surface 13S extends from radially inward relative to the outer peripheral edge 16E of the contact portion 16 to radially outward relative to the outer peripheral edge 16E, and is inclined toward the axial coil spring 1 as it extends radially outward. Therefore, when the coil spring 1 is compressed, the end turn portion 1B undergoes radial expansion and deformation as indicated by arrow A, causing a load perpendicular to the inclined surface 13S as indicated by arrow D to act on the inclined surface 13S. An axial load as indicated by arrow Da acts on the high-rigidity portion 13 as the axial component of the perpendicular load (arrow D). According to the support structure described above, this axial load (arrow Da) can increase the axial reaction force in the high reaction force portion 14, thereby more reliably approximating the center of the load input to the spring receiver 15 to the central axis O of the coil spring 1.

[0036] (4) In the above support structure, the inclination angle α of the inclined surface 13S with respect to the reference plane P is 45°. The inclination angle α is preferably 45° or greater. This allows the high-rigidity portion 13 to effectively generate an axial load (arrow Da) by utilizing the radial expansion deformation of the end turn portion 1B when the coil spring 1 is compressed.

[0037] (5) In the above support structure, the contact portion 16 extends over a range of 216° to 270° in the circumferential direction CD. If the range is less than 216°, the proportion of the contact portion 16 relative to the entire circumference of the spring receiver 15 decreases, resulting in a deterioration in the support rigidity of the coil spring 1. On the other hand, if the range is more than 270°, a sufficient inter-wire distance cannot be ensured at the starting end 1S, and there is a risk of inter-wire contact occurring at the starting end 1S when the coil spring 1 is compressed during vehicle travel. Inter-wire contact can damage the paint on the coil spring 1, causing corrosion and also being a source of abnormal noise.

[0038] Furthermore, the circumferential center point CP of the high reaction force portion 14 is located within a range of 108° to 135° in the circumferential direction CD from the starting end 1S. When the load applied to the coil spring 1 fluctuates while the vehicle is running, the position of the contact end 1E moves in the circumferential direction CD, increasing or decreasing the circumferential length of the contact portion 16. By positioning the high reaction force portion 14 so that the circumferential center point CP is located within the above range, it is possible to prevent excessive unbalanced load from acting on the spring receiver 15 even when the load on the coil spring 1 fluctuates.

[0039] <Modification of First Embodiment> In the first embodiment, the high reaction force portion 14 includes a high rigidity portion 13, and the high rigidity portion 13 has an inclined surface 13S. Specifically, the high rigidity portion 13 has a triangular cross-sectional shape in a cross section perpendicular to the circumferential direction CD. The high reaction force portion 14 according to the modification may include a high rigidity portion 13X without an inclined surface 13S, instead of or in addition to the high rigidity portion 13. The high rigidity portion 13X may have a rectangular cross-sectional shape, as shown in FIG. 7 . Even in this case, the above-described effects (1), (2), and (5) can be obtained.

[0040] Second Embodiment Next, a support structure according to a second embodiment will be described with reference to Figures 8 and 9. In the following description of the second embodiment, only configurations that differ from the preceding embodiment and modified examples will be described, and elements that have the same functions as elements already described in the preceding embodiment, etc. will be assigned the same reference numerals, and descriptions thereof will be omitted.

[0041] In this embodiment, the high reaction force portion 14 has a protrusion 17, as shown in Figures 8 and 9. The protrusion 17 is formed on the contact surface of the lower bearing case 9L, which serves as an insulator support member, with the insulator 11, and is made of, for example, hard resin. That is, the protrusion 17 has higher rigidity than the insulator 11. The protrusion 17 protrudes toward the insulator 11. The insulator 11 has a notch 18 formed therein to accommodate the protrusion 17. Therefore, the crushing allowance of the insulator 11 is relatively small in the high reaction force portion 14. Therefore, the axial reaction force per unit circumferential length in the high reaction force portion 14 is greater than in a case where the protrusion 17 is not provided.

[0042] The protrusion 17 has an inclined surface 17S. The inclined surface 17S extends from radially inward of the outer peripheral edge 16E (see FIG. 2) of the contact portion 16 to radially outward of the outer peripheral edge 16E, and is inclined so as to be positioned toward the axial coil spring 1 as it extends radially outward. The inclination angle of the inclined surface 17S with respect to a reference plane perpendicular to the axial direction of the coil spring 1 is equal to the inclination angle α of the inclined surface 13S. The configuration other than the high reaction force portion 14 is the same as in the first embodiment, and therefore description thereof will be omitted.

[0043] The effects of the support structure for the coil spring 1 according to the second embodiment will be described.

[0044] The second embodiment differs from the first embodiment in that the insulator 11 forms the high reaction force portion 14, in that the lower bearing case 9L, which is an insulator support member, forms the high reaction force portion 14. The second embodiment also differs from the first embodiment in that the high reaction force portion 14 includes a protrusion 17 formed on the lower bearing case 9L, in that the high reaction force portion 14 includes a high rigidity portion 13 embedded in the insulator 11. However, since the other configurations of the high reaction force portion 14 are the same as those of the first embodiment, the second embodiment can achieve at least the above-mentioned effects (1) and (5).

[0045] (7) In the above support structure, the spring bearing 15 includes the insulator 11 and the lower bearing case 9L, which is an insulator bearing member, and the lower bearing case 9L constitutes the high reaction force portion 14. Therefore, even if the insulator 11 deteriorates over time, the axial reaction force in the high reaction force portion 14 can be maintained high. In addition, the high reaction force portion 14 includes a protrusion 17 that protrudes toward the insulator 11 and is formed on the contact surface of the lower bearing case 9L with the insulator 11. Therefore, with the above support structure, the distribution of the axial reaction force in the circumferential direction CD can be adjusted with a simple configuration, and the center of the load input to the spring bearing 15 can be moved closer to the central axis O of the coil spring 1.

[0046] (8) In the above support structure, the protrusion 17 has an inclined surface 17S. The inclined surface 17S extends from radially inward of the outer peripheral edge 16E of the contact portion 16 to radially outward of the outer peripheral edge 16E, and is inclined so as to be positioned toward the axial coil spring 1 as it extends radially outward. Therefore, when the coil spring 1 is compressed, the end turn portion 1B expands and deforms, causing a vertical load to act on the inclined surface 17S. An axial load acts on the protrusion 17 as the axial component of this vertical load. With the above support structure, this axial load can increase the axial reaction force in the high reaction force portion 14, and the center of the load input to the spring receiver 15 can be more reliably moved closer to the central axis O of the coil spring 1.

[0047] (9) In the above support structure, the inclination angle of the inclined surface 17S with respect to the reference plane is 45°. The inclination angle is preferably 45° or more. This allows the projection 17 to effectively generate an axial load by utilizing the radial expansion deformation of the end turn portion 1B when the coil spring 1 is compressed.

[0048] <Modification of Second Embodiment> In the second embodiment, the high reaction force portion 14 includes a protrusion 17, which has an inclined surface 17S. Specifically, the protrusion 17 has a triangular cross-sectional shape in a cross section perpendicular to the circumferential direction CD. The high reaction force portion 14 according to the modification may include a protrusion 17X without an inclined surface 17S, instead of or in addition to the protrusion 17. As shown in FIG. 10 , the protrusion 17X may have a rectangular cross-sectional shape. Even in this case, the above-described effects (1), (5), and (7) can be obtained.

[0049] Other embodiments include a combination of the first embodiment and the second embodiment (including their modifications). In these other embodiments, it is possible to obtain the respective effects of the embodiments, etc., corresponding to the respective combined elements.

[0050] The above-described embodiments and modifications are merely examples described to facilitate understanding of the invention. The technical scope of the invention is not limited to the specific technical matters disclosed in the above-described embodiments, etc., but also includes various modifications, changes, alternative technologies, etc. that can be easily derived therefrom.

[0051] In the above embodiments, an example has been described in which the coil spring support structure of the present invention is applied to a strut-type suspension mechanism for steered wheels, but the support structure of the present invention can be applied to other types of suspension mechanisms. Furthermore, the support structure of the present invention may be applied not only to suspension mechanisms for steered wheels (e.g., front wheels), but also to suspension mechanisms for non-steered wheels (e.g., rear wheels).

[0052] REFERENCE SIGNS LIST 1 coil spring 1S starting end 9L lower bearing case (insulator support member) 11 spring insulator (insulator) 12 general portion 13, 13X high rigidity portion 13S inclined surface 14 high reaction force portion CP circumferential center point 15 spring support 16 contact portion 16E outer periphery 17 convex portion 17S inclined surface O central axis LS line segment L straight line P reference plane α inclination angle

Claims

1. A support structure for a coil spring of a vehicle suspension mechanism, comprising: a coil spring; and a spring support that receives one axial end of the coil spring, wherein the spring support has a contact portion extending circumferentially of the coil spring and that contacts the one end of the coil spring when the vehicle is stopped empty, and a high reaction force portion is provided in a portion of the contact portion other than both circumferential ends of the contact portion, and the high reaction force portion has higher rigidity than portions of the contact portion other than the high reaction force portion.

2. A support structure for a coil spring as described in claim 1, wherein the spring support comprises: an insulator contacting said one end of the coil spring; and an insulator support member provided on the opposite side of the insulator to the coil spring and contacting the insulator, and the insulator or the insulator support member constitutes the high reaction force portion.

3. A support structure for a coil spring as described in claim 2, wherein the insulator has a general portion and a high rigidity portion that is formed integrally with the general portion and has higher rigidity than the general portion, the circumferential end portion of the contact portion is composed of the general portion, the high reaction force portion comprises the high rigidity portion, and the high rigidity portion has an inclined surface, the inclined surface extending from a radially inner side of the coil spring relative to the outer circumferential edge of the contact portion to a radially outer side of the outer circumferential edge, and inclining so as to be positioned toward the coil spring in the axial direction as it moves toward the radially outer side.

4. A support structure for a coil spring as described in claim 2, wherein the high reaction force portion of the contact portion has a convex portion formed on the contact surface of the insulator support member with the insulator, the convex portion protruding toward the insulator.

5. A support structure for a coil spring as described in claim 4, wherein the convex portion has an inclined surface which extends from a radially inner side of the coil spring relative to the outer circumferential edge of the contact portion to a radially outer side of the outer circumferential edge, and which is inclined so as to be positioned toward the coil spring in the axial direction as it moves radially outward.

6. A support structure for a coil spring as described in any one of claims 2 to 5, wherein one of the circumferential ends of the contact portion is in contact with a starting end of the spiral of the coil spring, and when viewed in the axial direction, the contact portion extends over a range of 216° to 270° in the circumferential direction, and the circumferential center point of the high reaction force portion is located within a range of 108° to 135° from the starting end.

7. A support structure for a coil spring as described in claim 3 or 5, wherein the inclination angle of the inclined surface with respect to a reference plane perpendicular to the axial direction is 45° or more.

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