JP2003011602A - Wheel with spring unit - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a wheel with a spring unit reducing a clearance between a rim and a disk. SOLUTION: This wheel 1 with the spring unit comprises the rim 10, the disk 20 having a space relative to the rim, and the multiple spring units 30 having metal springs 34, disposed annually in the space, and having one ends connected to or abutting on a member 12 attached to a rim-side rib 11 projecting radially inward from the rim to the space inside or to the rim, and the other end connected to or abutting on a member 22 attached to a disk-side rib 21 projecting radially outward from the disk 20 to the space inside or to the disk.

Description

Detailed Description of the Invention

[0001]

TECHNICAL FIELD The present invention relates to a wheel with a spring unit for an automobile.

[0002]

2. Description of the Related Art Conventionally, as shown in FIG. 55, FIG. 56 or FIG. 57, FIG. 58, a rim 101 and a disk 102 are connected by an elastic body 103 to reduce road noise and harshness of a vehicle and to control the vehicle. Elastic wheels aiming to improve safety and motion controllability are known. Figure 5
5 and 56, the elastic body is rubber, and in FIGS. 57 and 58, the elastic body is a ring-shaped leaf spring. The elastic wheel requires a spring force that generates an in-plane force Fr and a circulating force Fc as shown in FIG. 59 in order to ensure the desired performance.
Here, the in-plane force is a diametrical spring force that tends to keep the disc toward the center of the rim. A dynamic damper whose mass is the rim is constructed by in-plane force to suppress road noise. The circulating force is a spring force in the disc rotation direction. As a result, compliance in the rotation direction is gained and harshness is suppressed. In addition, the driving force and the braking force are transmitted by this spring force, and the performance during vehicle motion control is improved.

[0003]

However, the conventional elastic wheel has the following problems A to F. A. There is a large gap between the rim and the disc. Rubber type Conventional rubber type elastic wheels obtain the desired elastic force by using the elastic force of rubber. When the vehicle weight is applied to this wheel, the upper and lower ends of the wheel are largely deformed as shown in FIG. The thickness d shown in the figure is necessary in order for the rubber to have the durability to cope with large deformation while obtaining the desired elastic force. Further, the hardness of the rubber of the elastic wheel is determined by the dynamic spring constant near 100 Hz for the purpose of reducing noise. However, as shown in FIG. 61, in the case of rubber, the dynamic spring constant increases as the frequency increases, so normal running In the middle (0 to 15 Hz), the spring stiffness is only about half that. As a result, the vertical movement of the rim becomes large during normal traveling, and the clearance between the rim and the disk needs to allow for that movement. If both of the above conditions are combined, the gap between the rim and the disk needs to be about 25 mm. In the leaf spring type leaf spring type elastic wheel, the spring is loaded not by bolting or welding but by riveting in order to alleviate stress concentration due to spring fixing and avoid spring deterioration due to welding heat. As shown in FIGS. 62 and 63, in the case of riveting, a structure in which a metal retainer 105 is sandwiched between the rim and the disk is not directly secured to the rim and the disc in order to prevent air leakage of the rim and facilitate assembly work. To take. As a result, a space corresponding to the thickness of the retainer is needed. Further, a space for riveting is required between the inside and outside retainers 105. Further, since this spring also has a spring action in the diametrical direction, it is necessary to look at the bending margin in the diametrical direction. When combined together, the required clearance between the rim and the disc is usually 25 mm or more. Other spring type (the main shaft of the spring is oriented in the diametrical direction) As shown in FIGS. 64 and 65, when another spring is used in the diametrical direction, a sufficient dimension in the bending direction is required for the durability of the spring. is necessary. The required size is larger than in the above case, and the required clearance between the rim and the disc is usually 40 mm or more.

B. Insufficient reliability of the elastic body. Rubber type The rubber type is deteriorated with time due to ultraviolet rays, ozone, chemicals such as salt, etc., and durability must be taken into consideration. Since it is made of a leaf spring type metal, there is no problem of deterioration over time, but as shown in FIG. 66, it is twisted and deformed against a large lateral force, and the spring characteristics become unstable. Further, when twisted, the local stress of the spring becomes high, and the spring is easily damaged. In this type, if the spring width is made large, the amount of twist is reduced, so the spring characteristics are stable and less likely to break. The leaf spring is excellent as a spring for an elastic wheel because it can transmit load, torque, and steering force in a well-balanced manner. However, it has not been used as a spring so much and reliability must be taken into consideration.

C. There is no fail-safe function in the torque direction. In a conventional elastic wheel in which a rim and a disc are connected by an elastic body, when the elastic body is damaged, the rim and the disc are disconnected and the driving / braking torque cannot be transmitted, and the vehicle stops on the road. That is, there is no fail-safe function in the torque direction of the wheels.

D. High cost. Rubber type: The equipment cost for vulcanization adhesion is high, and the processing time is long, so the cost is high. Leaf spring: A large retainer is required, and the spring is a special spring, so the cost is high. Further, since the assembling is difficult and takes time, the assembling cost is high.

E. As shown in FIG. 67, when the rigidity against the moment in the steering direction is low, even if the disc is turned and the direction of the disc is changed, the steering force escapes at the elastic portion and the rim is not stable. The direction of the (tire) does not change as well. As a result, the effectiveness of the rudder becomes poor, and the steering wheel angle when turning the same curve becomes large (poor effectiveness). On the other hand, if the steering moment rigidity of the rear wheels is low, the steering force of the rear wheels will be turned backwards by the lateral force during turning, and the rear wheels will not be supported and the vehicle will oversteer (swing). As a result, as shown in FIG. 68, the vehicle body slip angle increases, and a "engagement" feeling occurs. Although the above is the case of steering a large amount, when the small rudder is turned off quickly, the effectiveness of the rudder is delayed with time due to hysteresis (FIG. 69) due to internal friction of the elastic portion. As a result, there is a "effect delay" that the vehicle does not follow the fast steering. The poor effectiveness, entrainment, and delay of effectiveness are the three major operational safety problems of the elastic wheel. Rubber type If a rubber type elastic wheel with a conventional structure is made of a rubber hardness that meets the requirements of the elastic wheel, the spring up to the axle direction will also be soft, and the rigidity (static rigidity) against the steering moment will be low, resulting in "ineffectiveness". , "Entrainment" is large. Further, since there is internal friction peculiar to rubber, "effect delay" with respect to fast steering (1 to 5 Hz) is likely to occur. The leaf spring type leaf spring has a high steering rigidity because the axle direction spring is stiff even if the diametrical spring is softened if the width is sufficiently wide. Also, because it is made of metal, there is no delay due to internal friction.

F. Abnormal noise problem Since the rim and the disk of the elastic wheel move relative to each other when the vehicle is running, an abnormal noise occurs when there is a sliding portion. Attention should be paid to the contact points of the rim, elastic body, and disk. Since the rubber type adhesive structure absorbs relative movement in the rubber part, abnormal noise is unlikely to occur. Further, even when the stopper is operated, the rubber absorbs the vibration, so that it is hard to make an abnormal noise. The leaf spring type leaf spring is assembled by riveting for the reason described above. As shown in FIG. 70, since the rivet is loosely coupled, abnormal noise is likely to be produced due to sliding between the metals. If other spring-type springs are directly attached, abnormal noise will easily occur due to sliding. It is necessary to press the both ends of the spring with retainers to seal the movement. An object of the present invention is to provide a wheel with a spring unit that can solve at least one of the above problems A to F.

[0009]

The present invention which achieves the above object comprises the following wheel with a spring unit, as shown schematically in FIG. 29 and in detail in FIGS. (1) It has a rim 10, a disc 20 separated from the rim 10 (in the radial direction of the wheel), and a metal spring 34, and a plurality of them are arranged in an annular shape between the rim and the disc, and one end thereof is arranged. It is connected or abutted to a rim-side rib 11 or a member 12 attached to the rim, which projects radially inward from the rim 10 into the space, and the other end radially outward from the disc 20 into the space. Spring unit 3 connected or abutted to a disk-side rib 21 protruding to the side or a member 22 attached to the disk
Wheel 1 with spring unit consisting of 0. (2) The rim-side rib 11 and the disc-side rib 21
Or the member 12 attached to the rim and the member 22 attached to the disc are meshable with each other in the wheel rotation direction (1). (3) Stopper ribs 31 and 32 are provided separately from the rim-side ribs and the disc-side ribs in the wheel axial direction, and the rim-side ribs and the disc-side ribs are sandwiched by the stopper ribs from both sides in the wheel axial direction (1 ) Wheel with spring unit as described. (4) The wheel with a spring unit according to (3), wherein a lubricant ring is provided between the stopper rib and the rim-side rib. (5) The wheel with a spring unit according to (3), wherein a rubber bush is provided between the stopper rib and the rim-side rib. (6) The wheel with a spring unit according to (3), wherein a hard ball mechanism is provided between the stopper rib and the rim-side rib.

Wheel 1 with a spring unit according to the present invention
Thus, the problems A to F are solved as follows.
It will be described with reference to FIGS. 29 to 54. Annular arrangement of the spring units 30 A plurality of small spring units 30 are arranged side by side in an annular shape between the rim 10 and the disc. At that time, the elastic force of the spring is oriented in the circulation direction (FIG. 29). In addition, the spring is pre-compressed or tensioned (preloaded). If a pair of springs with the same characteristics is used, the preload will force the central rim to try to fit in the middle (Fig. 30). When the springs of this pair are arranged in a ring, the disc acts as a centripetal force toward the center of the rim. This centripetal force becomes the in-plane force required for the elastic wheel.

By adopting this structure, the following problems are solved. I. Since the acting direction of the spring is the circulation direction, a margin dimension may be taken in the circulation direction, and the margin dimension in the wheel diameter direction may be small. As a result, the required clearance between the rim and the disc is 10 to 1
2 mm, which is about half that of the conventional method. (Solution of Problem A) b. Since it is only necessary to expect elastic force in one direction for springs, coil springs, leaf springs, and other metal springs with a proven track record can be used. (Solution of Problem B) c. The cost is low because it consists of multiple small spring units of the same shape. (Solution of Problem D) d. Since metal springs can be used, there is no delay in rudder effectiveness due to internal friction of the elastic body. (Solution of Problem E above)

When using the rim / disc meshing mechanism spring unit, the reaction force is received by the ribs 11 and 21 parallel to the axle, and the ribs 11 and 21 are set to a height at which they mesh with each other in the wheel rotation direction (see FIG. 31, FIG. 32). Even if the spring unit 30 is damaged, the rib 1
Since 1 and 21 mesh with each other in the rotational direction, torque can be transmitted. Therefore, the situation in which driving and braking cannot be performed does not occur, and fail-safe as a wheel is guaranteed.
(Solution of Problem C)

Rim / disc meshing mechanism (hanger type spring) A tension spring does not use a retainer, and the spring is directly attached to the hanger brackets 12 and 22 (members 12 attached to ribs and members 22 attached to the disc, as shown in FIG. ) It is also possible to hang it on a hanger. (Embodiment 4 of the present invention) In this case, since there is no parallel rib, the hanger brackets 12 and 22 are set to a height that meshes with each other in the wheel rotation direction to provide a fail-safe mechanism in the rotation direction (FIGS. 34 and 35). .

Stopper ribs 31 and 32 are provided at positions slightly separated from both ends of the ribs 11 and 21 or the hanger brackets 12 and 22 that receive the spring force of the bag binding rib structure (see FIGS. 36 and 37). One of them 31 is made as part of the structure of the disc, while the other 32
Open so that it does not get in the way when assembling, and weld it to the disc after the parts are assembled. Stopper rib 3
1, 32 may be attached to either side of the disc or the rim. The ribs 11 and 21 or the brackets 12 and 22 which receive the spring force by the stopper ribs 31 and 32 are sandwiched from both sides in the wheel axial direction and sealed in the bag, and the movement of the disc and the rim in the wheel axial direction is restricted. . As a result, the steering rigidity is increased, and it is possible to eliminate poor steering effectiveness and involvement. (Solution of Problem E above)

Mechanism for suppressing sliding during turning-1. Slip mechanism As shown in FIGS. 38 and 39, the stopper ribs 31, 3
The inside of 2 is covered with a lubricant ring 33 made of polytetrafluoroethylene or the like to reduce play in the axial direction and prevent fretting wear due to sliding of the parallel ribs 11 and 21 and the stopper ribs 31 and 32. Relax the sound. If it is not necessary, this lubricant ring 33 may be omitted (Example 2 of the present invention).

-2. Rubber bush or stopper ribs 31, 3 as shown in FIG.
The rubber bush 50 is sandwiched between the spring contact ribs 11 and 21 or the bracket 2 to release the movement by shearing the rubber, thereby preventing friction noise and fretting wear. The rubber bush 50 has stopper ribs 31, 32.
Make a small hole on the side to fix it. Then, when it is assembled to the wheel, it is assembled by compression and pressed against the spring retaining ribs 11 and 21 or the bracket by the compressive stress of the rubber. A frictional force is generated by this pressing force, and the spring retaining ribs 11,
Since the contact position with the rubber is fixed even when 21 is moved, the mutual movement of the stopper ribs 31, 32 and the spring retaining ribs 11, 21 or the bracket can be escaped by the shear deformation of the rubber. In the case of this method, since there is no sliding portion, vibration or abnormal noise does not occur. An application of this method will be described later as Example 5 of the present invention.

-3. A ball (hard ball) mechanism or stopper ribs 31, 3 as shown in FIG.
2 and the stopper ribs 31 and 32 by rolling, by sandwiching a hard ball 51 between the stopper ribs 31 and 32 and the spring retainer ribs 11 and 21 or the bracket at the contact sliding portion between the spring retainer ribs 11 and 21 or the bracket. Friction noise is prevented by escaping the relative movement between the spring retaining ribs 11 and 21 or the bracket. This method reduces the resistance in the sliding direction (about 1/50 of that in the case of friction) to prevent vibration and noise. This method can maximize the lateral rigidity. (Solution of the above-mentioned problem F). The application of this method will be described later as Example 6 of the present invention.

Structure of Spring and Retainer (In case of compression spring) When the metal spring 34 is the coil type compression spring 34A, a retainer 35 having a recess corresponding to the diameter of the spring 34 as shown in FIGS. 42 to 44 is used. (Example 1). By setting the spring in the recess, sliding of the spring end can be stopped, and abnormal noise can be prevented (solution of the problem F). Instead of the recess, a spring seat having a protrusion protruding inward of the coil diameter of the spring may be used to firmly receive the spring. In addition, the plurality of springs 34 are bundled by the retainer 35 to form the spring unit 30.
As a result, the spring can be easily attached to the wheel (the problem D is solved). The metal spring 34 is the leaf spring 3
In the case of 4B, as shown in FIGS. 45 and 46, a retainer 35 having a long depression is used (Example 2). The spring portion may be integrated or divided. Coil spring 3
Since both 4A and the leaf spring 34B are used by preloading in the compression direction, there is no concern that they will come off the retainer 35. As shown in FIG. 47, the retainer 35 has an eaves 3 for covering the upper surfaces of the ribs 11 and 21.
Attach 6. This eaves 36 functions as a stopper that prevents overstroke when the spring unit 30 is largely bent by a large input. Further, the eaves 36 can alleviate abnormal noise when hitting the stopper (problem F
Solution).

Structure of Retainer (Case of Tension Spring) The retainer 35 of the tension spring has a hook 37 as shown in FIGS. 48 and 49 to fix the spring 34 (Example 3). Since the spring is always preloaded (pulling force), it does not come off and the position is unlikely to be displaced, so that abnormal noise is rarely generated (solution of the problem F). Further, since the plurality of springs 34 are bundled to form the spring unit 30, the assembling is easy (the solution of the problem D). The retainer 35 is provided with an eaves functioning as a stopper as in the case of the compression coil spring. Then, a claw 38 is provided at the tip of the eave and is hooked in the groove of the rim to receive the force of the spring. In the case of the hanger type of the fourth embodiment, the retainer is not provided and the plurality of springs 34 are provided.
Hook 12 directly onto the hangers 12 and 22 to assemble. Although the assembling process is complicated, there is an advantage that the number of parts is reduced (the problem D is solved).

The damping of the movement of the mounting rim of the damping component may be poor, and there may be a feeling of bubbling when passing over the protrusion. In such a case, a part of the spring is replaced by the hydraulic damper 39 (Fig. 51) and the friction damper 40 (Fig. 5).
2) Replace with rubber damper 41 (Fig. 53) or the like to obtain a damping force.

Assembling Method of Spring Unit The spring unit 30 must be assembled by preloading. The spring unit when not preloaded is longer than the rib circumferential gap in the compression type and short in the tension type. At the time of assembling, it is necessary to apply a force corresponding to the preload, which makes work more difficult than assembling without preload. To solve this, the following method is adopted. Compression type: As shown in FIG. 54, when the rim 10 is rotated with respect to the disk 20, the interval between the insertion portions can be increased by one step. In that state, half of the spring units 30 are loaded. Next, the spring is rotated in the opposite direction until the spring is fully bent, the gap between the other insertion portions is widened, and the remaining spring unit 30 is loaded.

[0022]

BEST MODE FOR CARRYING OUT THE INVENTION Wheels with spring units according to Embodiments 1 to 6 of the present invention will be described with reference to FIGS. Example 1 (FIGS. 1 to 6) In the wheel 1 with a spring unit of Example 1 of the present invention,
The metal spring 34 of the spring unit 30 is the compression coil spring 3
It consists of 4A. The spring characteristic of each spring 34A is as shown in FIG. Each spring unit 30 has a plurality of coil springs 34A arranged in parallel with each other, and has a plurality of coil springs 3A.
Each end of 4A is held by a resin retainer 35. Each spring unit 30 is preloaded on the compression side,
It is arranged in the space in the wheel circumferential direction between the rim-side rib 11 and the disc-side rib 21. One end of each spring unit 30 is subjected to a force by the rim-side rib 11 via the retainer 35, and the other end is connected to the disc-side rib 2 via the retainer 35.
You can get power in 1. Stopper ribs 31 and 32 are formed at a distance from both ends of the spring unit 30 in the axial direction of the wheel, and one stopper rib 32 is welded to the disc 20 after the spring unit 30 is loaded on the disc. Between the stopper ribs 31, 32 and the rim-side rib 11, a ring 33 made of a lubricant (for example, polytetrafluoroethylene) or a rubber bush 50,
Alternatively, hard balls 51 are arranged. Example 1 of the present invention
The action of is as described above.

Second Embodiment (FIGS. 7 to 12) In the wheel 1 with a spring unit according to the second embodiment of the present invention,
The metal spring 34 of the spring unit 30 is a compression leaf spring 34B.
Consists of. The spring characteristic of each spring 34B is as shown in FIG. Each end of the leaf spring 3BA of each spring unit 30 is held by a resin retainer 35. Each spring unit 30 is preloaded on the compression side, and the rim-side rib 11
And a disk-side rib 21 are arranged in a space in the wheel circumferential direction. One end of each spring unit 30 is received by the rim-side rib 11 via the retainer 35, and the other end is received by the disc-side rib 21 via the retainer 35. Stopper ribs 31 and 32 are formed at a distance from both ends of the spring unit 30 in the axial direction of the wheel, and one stopper rib 32 is welded to the disc 20 after the spring unit 30 is loaded on the disc. A ring 33 made of a lubricant (for example, polytetrafluoroethylene), a rubber bush 50, or a hard ball 51 is arranged between the stopper ribs 31 and 32 and the rim-side rib 11. Regarding the operation of the second embodiment of the present invention,
As described above.

Example 3 (FIGS. 13 to 15) In the wheel 1 with a spring unit of Example 3 of the present invention,
The metal spring 34 of the spring unit 30 is the tension coil spring 3
It consists of 4A. Each spring unit 30 has a plurality of coil springs 34A arranged in parallel to each other, and each end of the plurality of coil springs 34A is hooked on a resin retainer 35. Each spring unit 30 is preloaded on the tension side and is arranged in the wheel circumferential direction space between the rim side rib 11 and the disc side rib 21. Each spring unit 30
One end is subjected to the force by the rim side rib 11 via the retainer 35, and the other end is received by the disc side rib 21 via the retainer 35. Each end of the coil spring 34A is hooked on the retainer 35 at a hook 37 portion,
The retainer 35 is fixed to the rim-side rib 11 or the disc-side rib 21 by a claw 38. The stopper rib 3 is slightly separated from both ends of the spring unit 30 in the axial direction of the wheel.
1 and 32 are formed, and one stopper rib 32 is formed.
Is loaded on the disc 20 after the spring unit 30 is loaded on the disc. A ring 33 made of a lubricant (for example, polytetrafluoroethylene), a rubber bush 50, or a hard ball 51 is arranged between the stopper ribs 31 and 32 and the rim-side rib 11. The operation of the third embodiment of the present invention is as described above.

Embodiment 4 (FIGS. 16 to 18) In the wheel 1 with a spring unit according to Embodiment 4 of the present invention,
The metal spring 34 of the spring unit 30 is the tension coil spring 3
It consists of 4A. Each spring unit 30 has a plurality of coil springs 34A arranged in parallel with each other, and the ends of the plurality of coil springs 34A are directly connected to the hanger brackets 12, 22.
It is hooked on the hangers 42 and 43 of the member 12 attached to the rib and the member 22 attached to the disc. There is no retainer of Examples 1-3. Each spring unit 30 is preloaded on the tension side and is arranged in the wheel circumferential direction space between the rim side rib 11 and the disc side rib 21. Stopper ribs 31 and 32 are formed at a distance from both ends of the spring unit 30 in the axial direction of the wheel, and one stopper rib 32 is welded to the disc 20 after the spring unit 30 is loaded on the disc. A ring 33 made of a lubricant (for example, polytetrafluoroethylene) or the rubber bush 5 is provided between the stopper ribs 31, 32 and the hanger 42 or the rib 11.
0, or hard balls 51 are arranged. The operation of the fourth embodiment of the present invention is as described above.

Embodiment 5 (FIGS. 19 to 23) In the wheel 1 with a spring unit according to Embodiment 5 of the present invention,
The metal spring 34 of the spring unit 30 is the compression coil spring 3
It consists of 4A. Each spring unit 30 has a plurality of coil springs 34A arranged in parallel with each other, and each end of the plurality of coil springs 34A is held by a resin retainer 35. Each spring unit 30 is preloaded on the compression side and is arranged in the wheel circumferential direction space between the rim rib 11 and the disc rib 21. Each spring unit 30
One end is subjected to the force by the rim side rib 11 via the retainer 35, and the other end is received by the disc side rib 21 via the retainer 35. Stopper ribs 31 and 32 are formed at a distance from both ends of the spring unit 30 in the axial direction of the wheel, and one stopper rib 32 is welded to the disc 20 after the spring unit 30 is loaded on the disc. A rubber bush 50 is arranged between the stopper ribs 31, 32 and the rim-side rib 11. The operation of the fifth embodiment of the present invention is as described above.

Embodiment 6 (FIGS. 24 to 28) In the wheel 1 with a spring unit of Embodiment 6 of the present invention,
The metal spring 34 of the spring unit 30 is the compression coil spring 3
It consists of 4A. Each spring unit 30 has a plurality of coil springs 34A arranged in parallel with each other, and each end of the plurality of coil springs 34A is held by a resin retainer 35. Each spring unit 30 is preloaded on the compression side and is arranged in the wheel circumferential direction space between the rim rib 11 and the disc rib 21. Each spring unit 30
One end is subjected to the force by the rim side rib 11 via the retainer 35, and the other end is received by the disc side rib 21 via the retainer 35. Stopper ribs 31 and 32 are formed at a distance from both ends of the spring unit 30 in the axial direction of the wheel, and one stopper rib 32 is welded to the disc 20 after the spring unit 30 is loaded on the disc. Hard balls 51 are arranged between the stopper ribs 31 and 32 and the rim-side rib 11. Example 6 of the present invention
The action of is as described above.

[0028]

According to the wheel with a spring unit of the first aspect, since the plurality of spring units are arranged in a ring shape in the space between the rim and the disk, the gap between the rim and the disk can be reduced in the wheel radial direction. Further, since the spring is made of metal, the reliability of the spring is high. Also, since there is no vulcanization adhesion, the cost is low. Also, since a metallic spring can be used, it is possible to eliminate the delay in the effectiveness of the rudder, which is the case with rubber. According to the wheel with the spring unit of the second aspect, the rim-side rib and the disc-side rib, or the member attached to the rim and the member attached to the disc are engaged with each other in the wheel rotation direction. Even if the spring unit is damaged, the torque for driving and braking can be transmitted, and fail-safe can be guaranteed. According to the wheel with spring unit of claim 3, a stopper rib is provided apart from the rim side rib and the disc side rib in the wheel axial direction, and the rim side rib and the disc side rib are sandwiched by the stopper rib from both sides in the wheel axial direction. Therefore, a bag-stitching rib structure is provided, the movement of the disc and the rim in the axial direction of the wheel can be regulated, the steering rigidity can be increased, and poor steering effectiveness and entrainment can be eliminated. According to the wheel with spring unit of the fourth aspect, since the lubricant ring is provided between the stopper rib and the rim-side rib, abnormal noise and fretting at the contact sliding portion between the stopper rib and the rim-side rib can be prevented. It can be prevented.
According to the wheel with spring unit of claim 5, since the rubber bush is provided between the stopper rib and the rim side rib, abnormal noise and fretting at the contact sliding portion between the stopper rib and the rim side rib are prevented. it can. According to the wheel with spring unit of claim 6, since the ball mechanism is provided between the stopper rib and the rim side rib, abnormal noise and fretting at the contact sliding portion between the stopper rib and the rim side rib are prevented. it can.

[Brief description of drawings]

FIG. 1 is a front view of a part of a wheel with a spring unit according to a first embodiment of the present invention.

FIG. 2 is a sectional view taken along line AA of FIG.

FIG. 3 is a sectional view taken along line BB of FIG.

FIG. 4 is a plan view of a spring unit in FIG.

FIG. 5 is a front view of the spring unit shown in FIG. 4;

6 is a graph showing spring characteristics of the spring unit of FIG.

FIG. 7 is a front view of a part of the wheel with the spring unit according to the second embodiment of the present invention.

8 is a cross-sectional view taken along the line AA of FIG.

9 is a sectional view taken along line BB of FIG.

10 is a plan view of the spring unit in FIG. 7. FIG.

11 is a front view of the spring unit of FIG.

12 is a graph showing spring characteristics of the spring unit of FIG.

FIG. 13 is a front view of a part of the wheel with the spring unit according to the third embodiment of the present invention.

14 is a cross-sectional view taken along the line AA of FIG.

FIG. 15 is a sectional view taken along line BB of FIG.

FIG. 16 is a front view of a part of the wheel with the spring unit according to the fourth embodiment of the present invention.

17 is a cross-sectional view taken along the line AA of FIG.

18 is a sectional view taken along line BB of FIG.

FIG. 19 is a front view of a part of the wheel with the spring unit according to the fifth embodiment of the present invention.

20 is a cross-sectional view taken along the line BB of FIG.

21 is a cross-sectional view taken along the line AA of FIG.

22 is a side view of the rubber bush of FIG. 21. FIG.

FIG. 23 is a front view of the rubber bush of FIG. 22.

FIG. 24 is a front view of a part of the wheel with the spring unit according to the sixth embodiment of the present invention.

25 is a cross-sectional view taken along the line BB of FIG.

26 is a cross-sectional view taken along the line AA of FIG.

27 is a side view of the hard ball mechanism of FIG. 26. FIG.

28 is a front view of the hard ball mechanism of FIG. 26. FIG.

FIG. 29 is a schematic front view of a wheel with a spring unit according to the present invention (Examples 1 to 6).

30 is a partial front view showing the neutral position of one of the springs of FIG. 29. FIG.

31 is a cross-sectional view showing meshing of the ribs of FIG. 29 in the wheel rotation direction.

32 is a front view (sectional view taken along line AA of FIG. 31) of a part of the wheel of FIG. 29.

FIG. 33 is a perspective view of a rim / disk engagement mechanism in the case of a hanger type tension spring.

34 is a partial cross-sectional view of a wheel with a spring unit having the rim / disc engagement mechanism of FIG. 33. FIG.

35 is a cross-sectional view taken along the line AA in FIG. 34.

FIG. 36 is a partial cross-sectional view of a wheel with a spring unit having a bag binding rib structure.

37 is a cross-sectional view taken along the line AA of FIG. 36.

FIG. 38 is a partial cross-sectional view of a wheel with a spring unit having a bag binding rib structure and a lubricant ring.

39 is a cross-sectional view taken along the line AA of FIG. 38.

FIG. 40 is a partial cross-sectional view of a wheel with a spring unit having a rubber bush mechanism.

FIG. 41 is a partial cross-sectional view of a wheel with a spring unit having a hard ball mechanism.

FIG. 42 is a plan view of a structure of a spring and a retainer in the case of a compression spring.

43 is a front view of the structure of FIG. 42. FIG.

44 is a side view of the retainer having the structure shown in FIG. 42 as viewed from the spring side.

FIG. 45 is a plan view of a structure of a spring and a retainer in the case of a leaf spring type compression spring.

46 is a front view of the structure of FIG. 45. FIG.

FIG. 47 is a front view of a portion of a wheel loaded with a spring unit having a retainer with an eaves.

FIG. 48 is a plan view of the structure of a spring and a retainer in the case of a tension spring.

49 is a front view of the structure of FIG. 48. FIG.

FIG. 50 is a front view of a hooking structure of a spring, a retainer and a rib in the case of a tension spring.

FIG. 51 is a plan view of a spring unit having a damper in a structure of a spring and a retainer.

FIG. 52 is a cross-sectional view of a friction damper incorporated in the spring unit.

FIG. 53 is a sectional view of a rubber damper incorporated in the spring unit.

FIG. 54 is a partial cross-sectional view of the wheel showing a method of incorporating the spring unit into the wheel.

FIG. 55 is a cross-sectional view of a rubber elastic wheel.

FIG. 56 is a front view of half of the elastic wheel of FIG. 55.

FIG. 57 is a cross-sectional view of an elastic wheel having a leaf spring that continuously extends over the entire circumference.

FIG. 58 is a front view of half of the elastic wheel of FIG. 57.

FIG. 59 is a front view of a wheel showing spring characteristics required for the elastic wheel.

FIG. 60 is a cross-sectional view showing rubber deformation of a rubber elastic wheel.

FIG. 61 is a graph showing a change in frequency of a dynamic spring constant of rubber of a rubber elastic wheel with frequency.

FIG. 62 is a partial cross-sectional view of an elastic wheel having a leaf spring that continuously extends around the entire circumference.

FIG. 63 is a front view of a part of an elastic wheel having a leaf spring that continuously extends over the entire circumference.

FIG. 64 is a front view of a part of the elastic wheel showing various springs arranged with the main shaft oriented in the wheel radial direction.

65 is a cross-sectional view of a part of the elastic wheel in which a coil spring is loaded among the various springs in FIG. 64.

66 is a perspective view of a spring showing the deformation of the S-shaped spring of the various springs of FIG. 64.

FIG. 67 is a cross-sectional view of a wheel for explaining a poor steering stability (defective braking effect) of the elastic wheel.

FIG. 68 is a cross-sectional view of a wheel for explaining a poor steering operation (engagement) of the elastic wheel.

FIG. 69 is a graph showing a hysteresis characteristic for explaining poor steering stability (delay of effectiveness) of the rubber elastic wheel.

FIG. 70 is a cross-sectional view of a spring coupling portion for solving the abnormal noise problem of an elastic wheel having a leaf spring continuously extending around the entire circumference.

[Explanation of symbols]

1 Wheel with Spring Unit 10 Rim 11 Rib Side Rib 12 Member Attached to Rim (eg Hanger Bracket) 20 Disc 21 Disc Side Rib 22 Member Attached to Disc (eg Hanger Bracket) 30 Spring Unit 31, 32 Stopper Rib 33 Lubricant ring 34 Metal spring 34A Coil spring 34B Leaf spring 35 Retainer 36 Eave 37 Hook 38 Claw 39 Hydraulic damper 40 Friction damper 41 Rubber damper 42, 43 Hanger 50 Rubber bush 51 Hard ball mechanism

Claims (6)

[Claims] 1. A rim, a disc separated from the rim, and a metal spring, and a plurality of annular rings are arranged between the rim and the disc, one end of which is radially inward from the rim. It is connected to or abuts on the rim rib protruding into the space or a member attached to the rim, and the other end is attached to the disc rib protruding into the space radially outward from the disc or the disc. A wheel with a spring unit, which comprises a spring unit connected to or abutted on the member. 2. The rim-side rib and the disc-side rib, or the member attached to the rim and the member attached to the disc can mesh with each other in the wheel rotation direction. Wheel with spring unit. 3. The stopper rib is provided separately from the rim-side rib, the disc-side rib in the wheel axial direction, and the rim-side rib and the disc-side rib are sandwiched by the stopper rib from both sides in the wheel axial direction. Wheel with spring unit as described. 4. The wheel with a spring unit according to claim 3, wherein a lubricant ring is provided between the stopper rib and the rim-side rib. 5. The wheel with a spring unit according to claim 3, wherein a rubber bush is provided between the stopper rib and the rim-side rib. 6. The wheel with a spring unit according to claim 3, wherein a hard ball mechanism is provided between the stopper rib and the rim-side rib.