Upper mount

Abstract

To provide a compact upper mount capable of preventing the weight of a vehicle body from acting on a speed reduction mechanism and being easily operated.SOLUTION: A cylindrical fixed member 1 attached to a vehicle body B via an elastic member 1a, an operating member 2 rotatably supported by the fixed member 1, at least one planetary gears P provided in the operating member 2 and revolving around an axial center X of the operating member 2, the upper mount M includes a second member R2 having a second internal-gear R2 that meshes with the planetary gears P, and a first member R2 that can be raised and lowered with respect to the second member r1 via a threaded portion S centered on the axial center X, has a first internal-gear R11 that meshes with the planetary gears P, and has a spring receiving portion r1 that receives an upper end of a coil spring C that supports the vehicle body B.SELECTED DRAWING: Figure 3

Description

[Technical Field]

[0001] The present invention relates to an upper mount that is installed, for example, between a vehicle body and a coil spring and has a variable height dimension. [Background technology]

[0002] Conventionally, such an upper mount is disclosed, for example, in Patent Document 1 (see

[0011] ,

[0018] ,

[0033] and Figs. 1 and 2).

[0003] This upper mount has an annular upper spring seat 3 that receives the upper end of the coil spring 2, and a linear actuator 6 that changes the height position of the vehicle body 1 relative to the upper spring seat 3. The linear actuator 6 has an outer ring member 20 that is formed in a cylindrical shape extending downward from the inner periphery of the upper spring seat 3 inside the coil spring 2 and has a helical ridge 26 on its inner periphery, a rotating shaft 21 located at the center of the outer ring member 20, an electric motor 13 that rotates and drives the rotating shaft 21, and a plurality of planetary rollers 22 that are incorporated between the inner periphery of the outer ring member 20 and the outer periphery of the rotating shaft 21 and have a helical groove or circumferential groove 27 on their outer periphery that engages with the helical ridge 26.

[0004] In this configuration, vehicle height is adjusted by moving the upper support 7 and the upper spring seat 3 toward or away from each other using planetary rollers 22 driven by the electric motor 13. The planetary rollers 22 revolve around the rotation shaft 21 while rotating around the carrier pin 23A, reducing the rotation speed of the electric motor 13 and changing the height relative to the outer ring member 20. In particular, the equivalent lead angle of the planetary rollers 22 is set to 0.5° or less, so that the vehicle height can be maintained even without supplying power to the electric motor 13.

[0005] This device can generate the large linear driving force required for vehicle height adjustment without the need for a separate multi-stage reduction mechanism. In addition, the outer ring member 20 of the planetary roller mechanism is housed inside the coil spring 2, making it compact and easy to install on the vehicle body 1. [Prior art documents] [Patent documents]

[0006] [Patent Document 1] Japanese Patent Application Publication No. 2016-22837 Summary of the Invention [Problem to be solved by the invention]

[0007] In the above-mentioned conventional upper mount, the two shafts, the rotating shaft 21 and the piston rod 16, are arranged in series at different positions above and below. As a result, the suspension becomes longer by the length of the rotating shaft 21, which makes it less suitable for mounting on a vehicle.

[0008] Furthermore, since the vehicle weight is constantly acting on the entire planetary gear roller mechanism, including the planetary rollers 22, the size of the planetary roller mechanism must be increased to ensure its strength.

[0009] Furthermore, because the planetary roller mechanism also functions as a speed reducer, the vehicle weight is applied to the deceleration mechanism, which increases the frictional resistance of the reducer, and therefore requires a large input torque.

[0010] As described above, conventional upper mounts have various problems that need to be solved, and there has been a demand for an upper mount that is compact and easy to operate, and that does not cause the vehicle body weight to act on the reduction mechanism. [Means for solving the problem]

[0011] (Features and configuration) The upper mount according to the present invention has the following characteristic configuration: a cylindrical fixing member attached to a vehicle body via an elastic member; an operating member rotatably supported by the fixed member; At least one planetary gear is provided on the operating member and revolves around an axis of the operating member; a second member that is supported rotatably about the axis relative to the fixed member and has a second internal gear that meshes with the planetary gear; The first member is capable of being raised and lowered relative to the second member via a threaded engagement portion centered on the axis, has a first internal gear that meshes with the planetary gear, and has a spring receiving portion that receives the upper end of a coil spring that supports the vehicle body.

[0012] (effect) With this configuration, the planetary gears rotate when the operating member is rotated, and this rotation is transmitted to the first internal gear of the first member and the second internal gear of the second member. At this time, the rotation of the operating member is decelerated to actuate the first member and the second member, and the planetary gears etc. function as a speed reduction mechanism.

[0013] The first member on which the first internal gear is formed does not rotate because the coil spring is supported by the spring receiving portion. Therefore, the first internal gear is a fixed gear. For example, by changing the number of teeth of the first internal gear and the second internal gear, the first member and the second member rotate differentially via the threaded engagement portion. This changes the relative positions of the first member and the second member, adjusting the height of the upper mount.

[0014] The load of the vehicle body first acts on the fixed member and is then transmitted to the spring bearing portion via the second member, the threaded portion, and the first member. Therefore, the load is not transmitted to the reduction mechanism. This reduces frictional resistance between the components of the reduction mechanism, making it possible to adjust the vehicle height with a small input torque.

[0015] The reduction mechanism and the threaded portion are arranged coaxially with the coil spring, allowing for compactness, resulting in an upper mount that is easy to install on a vehicle.

[0016] Furthermore, for example, the operating member can be exposed in a service hole on the vehicle body side, eliminating the need to jack up the vehicle or remove and attach the tire wheel when adjusting the vehicle height.

[0017] (Features and configuration) In the upper mount of the present invention, the planetary gear comprises a second external gear that meshes with the second internal gear and a first external gear that meshes with the first internal gear, and it is advantageous if the module of the first external gear is different from the module of the second external gear.

[0018] (effect) In this upper mount, the operating member is rotated to rotate the first and second members relative to each other, changing the threaded state of the two. To achieve this, the modules of the first external gear and the second external gear are changed to create a difference in tooth size between them. These external gears mesh with an internal gear that has a reference circle diameter larger than the reference circle diameter of the external gear. By making the tooth sizes different, it becomes easier to create a difference in the number of teeth between the first internal gear and the second internal gear, increasing the degree of freedom in setting the operating rotation conditions of the first and second members.

[0019] (Features and configuration) In the upper mount according to the present invention, it is advantageous to set the number of teeth of the first external gear to be equal to the number of teeth of the second external gear, and to configure the teeth of the first external gear and the teeth of the second external gear to be in the same phase when viewed in a direction along the axis.

[0020] (effect) As in this configuration, by aligning the teeth of the first external gear with the teeth of the second external gear along the axis, assembly of the planetary gears becomes easy. When assembling the planetary gears to the first and second members, the first external gear and the first internal gear must mesh, and the second external gear and the second internal gear must mesh. Since the number of teeth of the first internal gear and the number of teeth of the second internal gear usually differ, when the teeth of both gears are viewed along the axis, the overlapping state of the internal teeth of both gears differs at each position along the circumferential direction. In this state, if the number of teeth or tooth phase differs between the first external gear and the second external gear, aligning the tooth phases of the first internal gear and the second internal gear becomes extremely complicated. Therefore, by configuring the first external gear and the second external gear as in this configuration, it is only necessary to identify the relative rotational phase between the first internal gear and the second internal gear at the position where the teeth of both gears are aligned along the axial direction, making it extremely easy to assemble the planetary gears.

[0021] (Features and configuration) In the upper mount according to the present invention, it is advantageous if the reference circle diameter of the second external gear is set smaller than the reference circle diameter of the first external gear p1.

[0022] (effect) In this upper mount, the planetary gears are attached to the operating member. However, because the planetary gears need to mesh with the first member that has the spring bearing portion, the planetary gears are provided below the upper mount.

[0023] When the planetary gears are configured to be attached from below the upper mount, it is easy to adjust the engagement between the first and second members to set the first and second internal gears to a predetermined relative phase and then mesh the planetary gears there. When meshing the planetary gears last in this way, it is simple to insert the planetary gears onto the planet gear shaft from the first member side toward the second member. To achieve this, the reference circle diameter of the second external gear at the rear in the insertion direction is configured to be smaller than the reference circle diameter of the first external gear.

[0024] The upper mount according to the present invention is also useful in a configuration in which a shock absorber is provided coaxially with the coil spring. In this case, the piston rod of the shock absorber can be inserted and fixed to the operating member.

[0025] By inserting and fixing the piston rod into the operating member, the shock absorber can be positioned concentrically with the coil spring. The operating member rotates when adjusting the height of the upper mount, but the piston rod also rotates relative to the shock absorber cylinder, so there is no particular inconvenience in inserting and fixing it. In fact, with this configuration, the shock absorber is positioned inside the coil spring, resulting in a suspension that is compact and easy to install on a vehicle.

[0026] Furthermore, by fixing the piston rod to the operating member, it becomes easier to maintain the axial position of the members that make up the upper mount, as described below. When a shock absorber is inserted into a coil spring, the shock absorber and coil spring change position relative to the vehicle body as they expand and contract while the vehicle is running. However, for example, because the operating member and the first member are maintained coaxially, the relative position of the planetary gear and the two internal gears is stable, which smooths the operation of the planetary gear mechanism and the threaded portions and reduces the risk of damage such as wear.

[0027] Furthermore, because the shock absorber and coil spring remain coaxially aligned during extension and contraction, the link members that make up the suspension are less likely to be twisted, and steering function is not impaired whether the upper mount supports the front or rear wheels. [Brief explanation of the drawings]

[0028] [Figure 1] FIG. 1 is an explanatory diagram showing a usage mode of an upper mount according to a first embodiment. [Figure 2] FIG. 1 is an exploded perspective view showing the configuration of an upper mount according to a first embodiment; [Figure 3]1 is a cross-sectional view showing an operation mode of an upper mount according to a first embodiment; [Figure 4] 10 is a cross-sectional view showing an operation mode of the upper mount according to the second embodiment. DETAILED DESCRIPTION OF THE INVENTION

[0029] [First embodiment] (overview) An example of an upper mount M according to a first embodiment of the present invention is shown in Figs. 1 to 3. The upper mount M is attached to the side of a vehicle body B, and supports the upper end of a coil spring C that constitutes a suspension. In the first embodiment, an example is shown in which the upper mount M is attached to the front wheel of a vehicle.

[0030] The upper mount M comprises a cylindrical fixed member 1 attached to the vehicle body B via an elastic member 1a, and a height adjustment portion H attached to the fixed member 1. The height adjustment portion H can be manually operated by the vehicle user when the vehicle is stopped, and changes the height position of the spring bearing portion R11 that receives the upper end of the coil spring C. Although the upper mount M cannot automatically adjust the vehicle height while driving, it is compact as it does not have any special electric drive unit, and is easy to attach to the vehicle and to adjust the height.

[0031] (fixing member) As shown in Figures 2 and 3, fixed member 1 is a cylindrical member that is fixed to a strut tower or the like formed on vehicle body B. An elastic member 1a made of a rubber material or the like is provided on the outer periphery of fixed member 1, and a fixed flange 1b is provided on the outer periphery of elastic member 1a. These are integrally formed, for example, by injection molding elastic member 1a between fixed member 1 and fixed flange 1b. Fixed flange 1b is fixed to a part of the strut tower with bolts 1c or the like. Supporting fixed member 1 via elastic member 1a allows for changes in the posture of coil spring C that occur when the wheel moves up and down, and also absorbs and mitigates vibrations transmitted from coil spring C to the vehicle.

[0032] As shown in Figure 3, the fixed member 1 is provided with a first bearing G1 inside itself that supports the rotation of the operating member 2, which will be described later. The main functions of the first bearing G1 are to center the operating member 2 relative to the fixed member 1 and to ensure smooth rotation. Therefore, for example, a general radial bearing using balls is used. Two first bearings G1 are provided along the direction of the axis X.

[0033] Additionally, a second bearing G2 is provided on the outer surface of the fixed member 1 to support the rotation of a second member R2 (described later). A portion of the load of the vehicle body B borne by the front wheels acts on the second bearing G2, and in this embodiment, a general radial bearing is used. By selecting the size of the balls in the radial bearing, the second bearing G2 can be inexpensively configured with a predetermined load-bearing capacity. Note that a thrust bearing with a higher load-bearing capacity may also be used.

[0034] (adjustment section) The height adjustment unit H raises and lowers the position of the first member R1 relative to the fixed member 1, adjusting the distance between the upper end of the coil spring C and the vehicle body B. In this embodiment, a planetary gear mechanism is used as the height adjustment unit H. In the planetary gear mechanism, the first member R1 and the second member R2 each serve as a ring gear equipped with an internal gear, and a planetary gear P, which is operated during the height adjustment operation, meshes with these ring gears. Details of these members are provided below.

[0035] As shown in Fig. 3, the operating member 2 rotates around the axis X, and its head is exposed at the center of the fixed member 1. A hexagonal operating portion 21, for example, is formed at the upper portion. On the other hand, an annular flange 22 is integrally formed at the end of the lower portion, and three planetary gear shafts 23, for example, are provided on the flange 22 parallel to the axis X. A planetary gear P is rotatably attached to each planetary gear shaft 23, and rotation of the operating member 2 causes each planetary gear P to revolve around the axis X.

[0036] The operating member 2 is fixed in position relative to the two first bearings G1 along the direction of the axis X. Specifically, the two first bearings G1 are arranged above and below each other, sandwiching an annular convex portion 11 formed on the inner surface of the fixing member 1, and a flange 22 abuts against the bottom of the lower first bearing G1. Furthermore, a fixing ring 24 engaged with the outer surface of the operating member 2 abuts against the top of the upper first bearing G1.

[0037] 3, a first external gear p1 and a second external gear p2 are formed adjacent to the planetary gear P. At least one planetary gear shaft 23 and one planetary gear P are provided, but if three or more are provided at equal intervals around the axis X in the circumferential direction, the coaxial state between the operating member 2 and the second member R2 described below and the like is well maintained.

[0038] The first external gear p1 is meshed with a first internal gear r1 formed on the inner surface of the first member R1. The second external gear p2 is meshed with a second internal gear r2 formed on the inner surface of the second member R2. The first internal gear r1 moves up and down relative to the first external gear p1 via a screw engagement portion S, which will be described later. For this reason, the first external gear p1 is configured to be longer along the direction of the axis X than the second external gear p2.

[0039] The module of the first external gear p1 and the module of the second external gear p2 are different, and the modules of the first internal gear r1 and the second internal gear r2 that mesh with them are also different. In this configuration, the teeth of the second external gear p2 and the second internal gear r2 are formed smaller than the teeth of the first external gear p1 and the first internal gear r1.

[0040] By varying the tooth sizes of both gears and appropriately setting their reference circle diameters, the range of tooth numbers that can be set for the gears with larger reference circle diameters, particularly the first internal gear r1 and the second internal gear r2, can be expanded, thereby increasing the degree of freedom in setting the differential rotation conditions between the first member R1 and the second member R2.

[0041] In this embodiment, the number of teeth of the first external gear p1 is equal to the number of teeth of the second external gear p2. Furthermore, when viewed in the direction along the axis X, the teeth of the first external gear p1 and the teeth of the second external gear p2 are configured to be in the same phase.

[0042] This configuration facilitates the assembly of the planetary gears P to the first member R1 and the second member R2, for example. In other words, the engagement rotation phases of the first member R1 and the second member R2 are determined so that the teeth of the first internal gear r1 and the teeth of the second internal gear r2 are in phase at the positions where the planetary gears P are engaged. When the planetary gears P are engaged with the first member R1 and the second member R2, it is easy to visually identify the positions where the phases of the teeth of both internal gears r1 and r2 are in phase, making the assembly of the planetary gears P simple and quick.

[0043] As shown in Fig. 3, the second member R2, which is a cylindrical member, has its upper end rotatably supported by the fixed member 1 via a second bearing G2. Meanwhile, at the lower end, a male threaded portion s2 is formed outside the position where the second internal gear r2 is formed. A female threaded portion s1 formed on the inner surface of the first member R1 is threadedly engaged with this male threaded portion s2. The male threaded portion s2 and the female threaded portion s1 form a threaded engagement portion S.

[0044] A second step portion R2a is formed near the upper end of the second member R2, and fits into the outer race of the second bearing G2. Normally, the thrust force of the coil spring C is transmitted to the second bearing G2 via the first member R1 and the second member R2. As a result, an upward external force is always acting on the second member R2. As a result, the second member R2 is always in contact with the second bearing G2, and the meshing state between the second external gear p2 and the second internal gear r2 is maintained.

[0045] The first member R1 is a substantially cylindrical member that houses the second member R2 and moves up and down relative to the second member R2 via the threaded portion S. An annular outer flange R1a that protrudes radially outward is provided at the lower end of the first member R1, and a spring bearing portion R11 that receives a coil spring C is formed on this flange. An annular inner flange R1b that protrudes toward the axis X is formed near the outer flange R1a, and a first internal gear r1 is formed on the inner edge of the inner flange R1b. By forming the first internal gear r1 at the lower end of the first member R1 in this manner, the vertical distance between the position of the female threaded portion s1 that threads with the male threaded portion s2 and the first internal gear r1 can be increased, thereby improving the postural stability of the first member R1.

[0046] The first member R1 moves up and down relative to the second member R2 by a distance traveled by the threaded engagement portion S. This distance of movement can be set appropriately depending on the characteristics of the vehicle on which the upper mount M is mounted. For example, the distance of movement of the upper mount M mounted on a vehicle that travels on rough roads will be greater than that of a vehicle that often travels on ordinary roads. The length of the first external gear p1 along the axis X is set to a length that can accommodate the movement of the first internal gear r1 up and down.

[0047] The inner flange R1b of the first member R1 serves as a stopper that abuts against the lower end of the second member R2 when the first member R1 moves upward. Meanwhile, a C-shaped stopper ring R1c, for example, is engaged with the inner surface of the upper end of the first member R1. This stopper ring R1c abuts against a male thread portion s2 formed on the outer surface of the lower part of the second member R2 when the first member R1 moves downward.

[0048] A spring sheet Cs made of, for example, rubber is interposed between the spring receiving portion R11 provided on the first member R1 and the coil spring C to absorb the impact acting from the coil spring C on the spring receiving portion R11.

[0049] (adjustment operation) FIG. 3 also shows the first member R1 moved to its upper and lower limit positions. The height adjustment operation is performed by manually rotating the operating member 2 with, for example, a specified wrench. As the operating member 2 rotates, the planetary gear P revolves around the axis X. The first internal gear r1, which meshes with the first external gear p1, is in contact with the coil spring C, and its rotation is restricted, making it a fixed gear. Therefore, the first external gear p1 rotates based on the rotation angle of the operating member 2, and the second external gear p2 rotates along with it.

[0050] As the second external gear p2 rotates, the second internal gear r2 meshing therewith rotates. In this embodiment, the second external gear p2 and the second internal gear r2 have smaller modules and reference circle diameters than the first external gear p1 and the first internal gear r1. By appropriately setting these modules and reference circle diameters, the second internal gear r2 rotates relative to the first internal gear r1 as the planetary gear P rotates. Note that by selecting the reference circle diameter, etc., the rotation direction of the second internal gear r2 with respect to the rotation direction of the operating member 2 can be set to either forward or reverse.

[0051] The degree of relative rotation of the second member R2 with respect to the first member R1 can be any value, for example, several degrees to several tens of degrees per rotation of the operating member 2. The rotational operation of the operating member 2 is decelerated and the second member R2 rotates differentially with respect to the first member R1, which means that the planetary gear P or the like functions as a speed reduction mechanism. In this embodiment, the thread pitch of the threaded portion S is appropriately set, so that the second member R2 does not rotate relative to the first member R1 due to reverse input from the coil spring C to the first member R1.

[0052] The load of the vehicle body B acts on the fixed member 1 and is transmitted to the coil spring C via the second member R2, the threaded portion S, and the first member R1. Therefore, the load is not transmitted to the reduction mechanism. This reduces frictional resistance between the components of the reduction mechanism, reducing the input torque for vehicle height adjustment. Furthermore, the required strength of the planetary gear P, first internal gear r1, and second internal gear r2 is reduced, allowing for downsizing while maintaining the durability of the components.

[0053] The reduction mechanism and the threaded portion S are arranged coaxially with the coil spring C, allowing for compactness, resulting in an upper mount M that is easy to install on a vehicle. Furthermore, for example, the operating member 2 can be exposed in a service hole in the vehicle body B, eliminating the need to jack up the vehicle or remove and install the tire wheel when adjusting the vehicle height.

[0054] (Assembly mode) The upper mount M of this embodiment can be assembled outside the vehicle in advance. Specifically, first, the fixed flange 1b, the elastic member 1a, and the fixed member 1 are integrally molded in advance. Next, the second bearing G2 is attached to the fixed member 1, and the second member R2 is fitted to this second bearing G2. The first member R1 is threadedly engaged with the second member R2 in advance, and a C-shaped stopper ring R1c is engaged with one end of the first member R1. At this time, the threading height of the first member R1 relative to the second member R2 is arbitrary.

[0055] Two first bearings G1 are fitted into the inner periphery of the fixed member 1, and the operating member 2 is inserted into both first bearings G1 from the first member R1 side. A fixed ring 24 is locked onto the outer periphery of the operating member 2 protruding from the upper first bearing G1.

[0056] Next, the state of the first internal gear r1 and the second internal gear r2 is observed to confirm the position where the phases of the teeth of both gears are aligned. The operating member 2 is rotated so that the three planetary gears P are positioned at this point, and the planetary gears P are inserted onto their respective planetary gear shafts 23. The reference circle diameter of the second external gear p2 is smaller than that of the first external gear p1, making it easy to insert the planetary gears P. A C-shaped clip 23a, for example, is fastened to the outer circumferential surface of the planetary gear shaft 23 protruding from the planetary gear P to prevent the planetary gears P from coming loose.

[0057] In the upper mount M of this configuration, the planetary gears P are attached to the operating member 2. However, the planetary gears P need to mesh with the first member R1 having the spring receiving portion R11, and the planetary gears P are attached below the operating member 2.

[0058] Meanwhile, the first external gear p1 of the planetary gear P is meshed with the first internal gear r1, and the second external gear p2 is meshed with the second internal gear r2. To adjust the phase of these gears, the first member R1 and the second member R2, which are meshed with each other, are rotated relative to each other. It is easy to set the first internal gear r1 and the second internal gear r2 to a predetermined relative phase and then mesh the planetary gear P with this. In this way, to mesh the planetary gear P later, it is simple to insert the planetary gear P onto the planet gear shaft 23 from the first member R1 side toward the second member R2. To achieve this, it is convenient to configure the reference circle diameter of the second external gear p2, which is located at the rear in the insertion direction, to be smaller than the reference circle diameter of the first external gear p1.

[0059] When the upper mount M of this embodiment is used in a front suspension, the operating member 2 can be operated, for example, from a service hole in the front strut tower in the engine compartment. When used in a rear suspension, the operating member 2 can be operated from a service hole in the rear strut tower in the luggage compartment. Therefore, the upper mount M of this embodiment makes it possible to easily adjust the vehicle height without jacking up the vehicle or removing and installing tires.

[0060] Second Embodiment FIG. 4 shows an upper mount M according to a second embodiment of the present invention. In this embodiment, a shock absorber 3 is provided as a suspension, coaxially aligned with a coil spring C. A hole 25 is formed in the center of the operating member 2, through which a rod 31 of the shock absorber 3 is inserted. A small-diameter portion 31a is formed at the end of the rod 31 via a step 31b. The small-diameter portion 31a is inserted into the hole 25, and a fixing nut 33 is attached to a male thread 32 formed at the portion protruding from the hole 25, thereby fixing the rod 31 to the operating member 2. At this time, the fixing nut 33 may be tightly tightened to unite the operating member 2 and the small-diameter portion 31a. Because the rod 31 is rotatable relative to the cylinder 30, this does not cause any problems with subsequent rotation of the operating member 2 or the function of the shock absorber 3.

[0061] In this embodiment, after the planetary gear P is attached, a cylindrical rubber receiver 27 is fitted into a recess 26 formed on the inner surface of the operating member 2. An abutment flange 27a that expands radially outward is formed at the lower end of this rubber receiver 27. The abutment flange 27a can abut against a bump rubber 34 that is disposed around the rod 31 of the shock absorber 3. When the shock absorber 3 is fully compressed, the bump rubber 34 acts as a buffer between the upper mount M and the cylinder 30, absorbing the impact transmitted from the cylinder 30 to the upper mount M.

[0062] Other configurations such as the planetary gear P, the first member R1, the second member R2, and the fixed member 1 are the same as those in the first embodiment.

[0063] As in this embodiment, by inserting and fixing the rod 31 of the shock absorber 3 into the operating member 2, the shock absorber 3 can be arranged concentrically with the coil spring C. The operating member 2 rotates when adjusting the height of the upper mount M, but the rod 31 also rotates relative to the cylinder 30 of the shock absorber 3, so no particular inconvenience occurs with this insertion and fixation. In fact, with this configuration, the shock absorber 3 is arranged inside the coil spring C, making it possible to configure a suspension that is compact and easy to install on a vehicle.

[0064] Furthermore, by fixing the rod 31 to the operating member 2, it becomes easier to maintain the positions of the members that make up the upper mount M around the axis X, as described below. In a configuration in which the shock absorber 3 is inserted into the coil spring C, the posture of the shock absorber 3 and the coil spring C changes relative to the vehicle body B as the shock absorber 3 expands and contracts while the vehicle is running. However, at that time, the state in which they share the axis X is maintained. In other words, because the operating member 2 and the first member R1 that make up the upper mount M are maintained coaxially with each other around the axis X, the relative posture of the planetary gear P and the two internal gears r1 and r2 is stable, making it less likely that the planetary gear mechanism or the threaded engagement portion S will be damaged.

[0065] Furthermore, since the shock absorber 3 and the coil spring C are well maintained in a coaxial state during extension and contraction, the steering function is not impaired whether the upper mount M supports the front wheels or the rear wheels.

[0066] As described above, the upper mount M of this configuration can be used with a wider range of suspension types, making it possible to obtain an upper mount M with greater versatility. [Industrial Applicability]

[0067] The upper mount of the present invention is applicable to vehicles in which the body is supported by coil springs, and can be widely used as a height-adjustable suspension member in a great number of vehicles. [Explanation of symbols]

[0068] 1 Fixing member 1a Elastic member 2 Operating member B body C. Coil spring M upper mount P planetary gear p1 First external gear p2 Second external gear R1 First member R11 spring bearing r1 First internal gear R2 Second member r2 Second internal gear S threaded part X-axis center

Claims

1. a cylindrical fixing member attached to a vehicle body via an elastic member; an operating member rotatably supported by the fixed member; At least one planetary gear is provided on the operating member and revolves around an axis of the operating member; a second member that is supported by the fixed member so as to be rotatable about the axis and has a second internal gear that meshes with the planetary gear; an upper mount comprising: a first member that can be raised and lowered relative to the second member via a threaded engagement portion S centered on the axis, that has a first internal gear that meshes with the planetary gear, and that has a spring receiving portion that receives the upper end of a coil spring that supports the vehicle body.

2. 2. An upper mount as described in claim 1, wherein the planetary gear comprises a second external gear meshing with the second internal gear and a first external gear meshing with the first internal gear, and the module of the second external gear is different from the module of the first external gear.

3. 3. An upper mount according to claim 2, wherein the number of teeth of the second external gear and the number of teeth of the first external gear are set equal, and the teeth of the second external gear and the teeth of the first external gear are configured to be in the same phase when viewed in a direction along the axis.

4. 4. The upper mount according to claim 2, wherein a reference circle diameter of the second external gear is set smaller than a reference circle diameter of the first external gear.

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