JPH0678619U - Intermediate bearing device - Google Patents

Abstract

(57) [Abstract] [Purpose] An intermediate bearing device equipped with an insulator consisting of two rubber-like elastic bodies was provided with a second rubber-like elastic body with uniform rigidity in the direction perpendicular to the axis of the rotating shaft. An intermediate bearing device is provided. [Structure] An insulator 29 including two annular rubber-like elastic bodies 38, 40 provided on the outer peripheral side of an intermediate bearing 28 attached to a rotating shaft is provided, and one rubber-like elastic body 40 has a strip plate shape. An intermediate bearing device formed in an annular shape by joining the overlapping portions 42 formed on both ends of the forming material to each other, and the width dimension of the overlapping portion 42 is a portion other than the overlapping portion 42. The width was set smaller than the width.

Description

[Detailed description of the device]

[0001]

[Industrial applications]

 The present invention relates to an intermediate bearing device equipped with an insulator made of two rubber-like elastic bodies, and is particularly suitable for application to an automobile propulsion shaft.

[0002]

[Prior art]

 In front engine / rear wheel drive type automobiles, a long propulsion shaft that connects the engine mounted on the front part of the vehicle body and the rear wheel mounted on the rear part of the vehicle body is used. The power from the engine is transmitted to the rear wheels.

When adopting such a long propulsion shaft, it is common practice to insert an intermediate bearing device in the middle of the propulsion shaft for smooth power transmission. It is already well known in Japanese Patent Publication No. 47-19929, Japanese Utility Model Laid-Open No. 58-48531 and the like.

FIG. 12 shows a sectional structure of a main part of such a conventional intermediate bearing device. That is, the intermediate bearing 2 attached in the middle of the rotating shaft 1 is attached with the first rubber-like elastic body 4 in an annular shape in which the outer peripheral edge portions are joined to the pair of front and rear insulator holders 3, and further. On the outer circumference of the first rubber-like elastic body 4 located between the pair of front and rear insulator holders 3, a second rubber-like elastic body 5 having an annular shape with a spring constant different from that of the first rubber-like elastic body 4 is provided. It is installed. A bearing bracket (not shown) connected to a vehicle body panel (not shown) is fitted in the insulator holder 3 described above.

Therefore, the rotating shaft 1 is rotatably suspended from the vehicle body panel by the intermediate bearing 2 via the insulator composed of the two rubber-like elastic bodies 4 and 5, and the displacement amount in the radial direction of the rotating shaft 1 is increased. The rotating shaft 1 is elastically supported via an insulator having a non-linear so-called two-stage spring constant, and vibrations from the rear wheels that move up and down with respect to the unevenness of the road surface are generated by this intermediate bearing device. It is designed so that it will not be transmitted to the vehicle body frame side via.

By the way, as shown in FIG. 13 showing the appearance of the conventional second rubber-like elastic body 5 shown in FIG. 12 and FIG. 14 showing its developed shape, as shown in FIG. Elastic material The superposed portions 7 are formed at both ends of the raw material 6, and the second rubber-like elastic body 5 having an annular shape is formed by joining the superposed portions 7 to each other with an adhesive or the like. To form.

[0007]

[Problems to be solved by the device]

 The second rubber-like elastic body 5 forming a part of the insulator in the conventional intermediate bearing device shown in FIGS. 12 and 13 has a uniform width dimension and the like throughout its entire area. Although it is considered that the spring constant is obtained, since the spring constant at the part of the adhesive layer 8 formed by the adhesive formed on the overlapping part 7 is generally larger than the spring constants at other parts, The spring constant in the direction perpendicular to the axis of the shaft 1 becomes uneven.

In addition to the cause of the adhesive layer 8 as described above, when the second rubber-like elastic body 5 is formed of a porous foam material or the like, in order to prevent water or the like from entering, It is necessary to form the surface of the second rubber-like elastic material 6 in advance to be smooth. Therefore, the rigidity differs between the surface texture of the second rubber-like elastic material 6 and its internal texture, and the surface texture along the direction perpendicular to the axis of the rotating shaft 1 has four layers. The spring constant of the part 7 is generally larger than the spring constant of the part other than the superposed part 7 where the surface texture has only two layers, and the spring constant in the direction perpendicular to the axis of the rotating shaft 1 is non-uniform. Will be.

In any case, when attaching the second rubber-like elastic body 5 to the outer peripheral surface of the first rubber-like elastic body 4 between the pair of front and rear insulator holders 3, or when the insulator holder 3 is mounted. When fixing the bearing bracket to the vehicle body panel side, it is necessary to perform work while confirming that the overlapping portion 7 of the second rubber-like elastic body 5 is at the preset position, which is extremely inferior in workability. .

Further, since the spring constant of the overlapping portion 7 becomes larger than the spring constant at the time of designing the second rubber-like elastic body 5, it is not possible to obtain an insulator having desired characteristics. However, there are problems such as being easily affected by the vibration from the rotary shaft 1.

Moreover, since the second rubber-like elastic body 5 has a simple annular shape, for example, when it is desired to change the rigidity in the direction of the load, the conventional second rubber-like elastic body 5 is used. The body 5 cannot fundamentally meet such a request.

[0012]

[The purpose of the device]

 A first object of the present invention is to provide an intermediate bearing device including an insulator made of two rubber-like elastic bodies, and a second rubber-like elastic body having a uniform rigidity in a direction perpendicular to the axis of the rotating shaft. An object is to provide an intermediate bearing device.

A second object of the present invention is to provide an intermediate bearing device including a second rubber-like elastic body whose rigidity differs depending on the direction of load as necessary.

[0014]

[Means for Solving the Problems]

 An intermediate bearing device according to a first aspect of the present invention comprises an insulator made of two annular rubber-like elastic bodies provided on the outer peripheral side of an intermediate bearing attached to a rotary shaft, and one of the rubber-like elastic bodies is provided. An intermediate bearing device, which is formed into an annular shape by joining the overlapping portions formed at both ends of a material whose body is a strip plate to each other, and the width dimension of the overlapping portion is the overlapping portion. It is characterized in that it is smaller than the width of other parts.

An intermediate bearing device according to a second aspect of the present invention includes an insulator made of two rubber-like elastic bodies each having an annular shape and provided on the outer peripheral side of the intermediate bearing attached to the rotary shaft. An intermediate bearing device formed in an annular shape by joining the overlapping portions formed on both ends of a material having the rubber-like elastic body in the form of a strip plate to each other. The feature is that a lightening portion is formed in the mating portion.

Further, the intermediate bearing device according to the third aspect of the present invention includes two insulators each made of a rubber-like elastic body and formed on the outer peripheral side of the intermediate bearing attached to the rotary shaft. The rubber-like elastic body is formed with a notch along its circumferential direction.

[0017]

[Action]

 According to the present invention, the vibration from the rotating shaft side is absorbed by the elastic deformation of the two rubber-like elastic bodies forming the insulator.

According to the first aspect of the present invention, the width dimension of the overlapping portion of one rubber-like elastic body is set to be smaller than the width dimension of the portion other than this overlapping portion, The spring constant in the direction perpendicular to the axis becomes uniform over the entire circumference of this one rubber-like elastic body.

Further, according to the second aspect of the present invention, the lightening portion formed in the overlapping portion of the one rubber-like elastic body reduces the rigidity of the overlapping portion, and as a result, the shaft of the rotary shaft is rotated. The spring constant in the direction perpendicular to the center is uniform over the entire circumference of this one rubber-like elastic body.

On the other hand, according to the third aspect of the present invention, one rubber-like elastic body is formed with a notch along the circumferential direction thereof, and the rigidity of the portion where the notch is formed is cut. It becomes lower than the rigidity of the part where the notch is not formed.

[0021]

EXAMPLE FIG. 1 shows a fracture structure of an example in which the intermediate bearing device according to the first embodiment of the present invention is applied to a propulsion shaft of a front engine / rear wheel drive type automobile. That is, a plurality of output side damper mounting portions 12 are radially provided at the rear end portion of the drive spline cylinder 11 slidably fitted to a transmission output shaft (not shown). Further, the base end portion of the input side joint bracket 14 is press-fitted into the tip of the hollow first propulsion shaft 13 arranged coaxially with the drive spline cylinder 11, and by welding these, the first thrust is achieved. The shaft 13 and the input side joint bracket 14 are integrally joined. The input side joint bracket 14 is provided with a plurality of input side damper mounting portions 15 which are radially offset from the output side damper mounting portion 12 of the drive spline cylinder 11 in a radial manner.

The damper mounting portions 12 and 15 are connected to each other via a flexible shaft joint 16. The specific structure of the flexible shaft coupling 16 is well known in, for example, Japanese Utility Model Laid-Open No. 4-185453, and is a cylindrical shape fixed to the damper mounting portions 12 and 15 via bolts 17 and nuts 18, respectively. A plurality of pairs of damper links 20, 21 whose both ends are alternately inserted into these collars 19 so as to straddle the collar 19 and the adjacent output side damper mounting portion 12 and input side damper mounting portion 15 respectively. The main part is constituted by and, so that the driving force of the drive spline cylinder 11 is transmitted from the output side damper mounting section 12 to the first propulsion shaft 13 side by the input side damper mounting section 15 via the damper links 20 and 21. It has become.

Here, since the damper links 20 and 21 are elastically deformable in the rotational direction of the drive spline cylinder 11 and the first propulsion shaft 13, the rotational unevenness of the drive spline cylinder 11 is absorbed. Is transmitted to the first propulsion shaft 13 side. The damper links 20 and 21 are elastically deformable in the radial direction of the bolt 17 (vertical direction in FIG. 1) and in the direction parallel to the longitudinal direction of the bolt 17 (horizontal direction in FIG. 1). The power can be transmitted in a state where the relative inclination of the drive spline cylinder 11 with respect to the one propulsion shaft 14 is allowed.

An aligning pin 22 is provided at the tip of the input side joint bracket 14 so as to project coaxially with the first propulsion shaft 13. Further, the base end portion of a cylindrical aligning sleeve 23 whose front end side surrounds the aligning pin 22 is press-fitted into the tip end portion of the drive spline 11, and by welding these together, the drive spline 11 is aligned. The core sleeve 23 is integrally joined. An aligning bush 24, which constitutes a spherical bearing, is interposed between the aligning sleeve 23 and the aligning pin 22, whereby the axial center of the drive spline cylinder 11 and the first propulsion. The shaft 13 is aligned so as not to be eccentric with the shaft center.

On the other hand, at the rear end of the first propulsion shaft 13, the front end side of the connecting shaft portion 25 is coaxially press-fitted, and by further welding these, the first propulsion shaft 13 and the connecting shaft portion 25. And are integrally joined. The tip end of the connecting cylinder 26 is spline-fitted to the tip end side of the connecting shaft portion 25, and the connecting nut 26 is screwed into the rear end of the first propulsion shaft 13 so that the connecting cylinder 26 is attached to the first propulsion shaft 13. In contrast, they are integrally connected. An intermediate bearing 28 is attached to the central portion of the connecting shaft portion 25, and an insulator 29 described later is provided on the outer peripheral side of the intermediate bearing 28. Further, a ring-shaped insulator holder 30 to which the outer peripheral edge of the insulator 29 is joined is fitted with a bearing bracket (not shown) fixed to the vehicle body panel side such as a floor pan (not shown), whereby the connecting shaft portion is connected. 25 is in a state of being rotatably suspended by an intermediate bearing 28 from the vehicle body panel via an insulator 29.

Further, one end side of a universal joint 33 is connected to the rear end portion of the connecting cylinder 26 via a bolt 31 and a nut 32, and the universal joint 33 is connected to the front end of the hollow second propulsion shaft 34. The parts are press-fitted and welded to each other, whereby the universal joint 33 and the second propulsion shaft 34 are integrally joined. Similarly, a universal joint 35, whose rear end is connected to a drive pinion shaft (not shown) whose rear end is connected to a rear wheel actuator (not shown), is press-fitted to the rear end of the second propulsion shaft 34, and by welding these together. The second propulsion shaft 34 and the universal joint 35 are integrally joined.

Therefore, the positional deviation between the transmission output shaft side (not shown) and the first propulsion shaft 13 is absorbed by the elastic deformation of the flexible shaft coupling 16, and the upper and lower movements of the rear wheel via the suspension device (not shown) occur. The driving force from the drive spline cylinder 11 side is absorbed by the relative movement of the pair of universal joints 33, 35 and the transmission output shaft and the drive spline cylinder 11 spline-fitted to the transmission output shaft. It is transmitted to the rear wheel differential gear side via the propulsion shaft 13 and the second propulsion shaft 34.

FIG. 2 shows an extracted enlarged sectional shape of a portion of the intermediate bearing device in this embodiment. That is, on the outer ring side of the intermediate bearing 28, the inner ring side of which is fitted to the connecting shaft portion 25 of the first propulsion shaft 13, a cylindrical outer ring receiver 36 is integrally fitted by press fitting or the like. In order to hold the intermediate bearing 28 with respect to the outer ring receiver 36, a cylindrical outer ring stopper 37 is attached to one end portion (the right end portion in the drawing) of the outer ring receiver 36 in an engaged state. Further, an inner peripheral surface of an elastically deformable annular first rubber-like elastic body 38 formed of rubber or the like is integrally bonded to the outer peripheral surface of the outer ring receiver 36 by vulcanization adhesion or the like, Flexible portions 39 that can be flexibly deformed are formed on both front and rear sides of the first rubber-like elastic body 38, and a pair of front and rear insulator holders 30 forming an annular shape are provided on the outer circumference of these flexible portions 39. Are integrally joined by vulcanization adhesion or the like.

On the outer periphery of the first rubber-like elastic body 38 located between the front and rear insulator holders 30, a second rubber-like elastic body having an annular shape having a smaller spring constant than the first rubber-like elastic body 38 is formed. The elastic body 40 is held in a state of being sandwiched between the flexible portions 39. Then, the insulator 29 including the first rubber-like elastic body 38 and the second rubber-like elastic body 40 elastically deforms according to the displacement amount of the connecting shaft portion 25, and the propulsion shafts 13, 33 side to the vehicle body panel side. The transmitted vibration is efficiently reduced.

FIG. 2 and FIG. 3 showing the appearance of the second rubber-like elastic body 40 in the present embodiment and its developed shape are shown in FIG. That is, the overlapping portions 42 are formed on both ends of the second rubber-like elastic material 41 in the form of a strip, and these overlapping portions 42 are joined to each other with an adhesive or the like. Thus, the second rubber-like elastic body 40 is formed. The width dimension of the overlapping portion 42 of the second rubber-like elastic body 40 is set to be smaller than the width dimension of the portion other than the overlapping portion 42, and specifically, the overlapping portion 42 formed by the adhesive layer 43. The width of the overlapping portion 42 is set small so that the rigidity of the overlapping portion 42 is canceled out, that is, the rigidity of the overlapping portion 42 is equal to the rigidity of the portions other than the overlapping portion 42. It

As a result, the rigidity of the second rubber-like elastic body 40 in the direction perpendicular to the axis of the connecting shaft portion 25 of the first propulsion shaft 13 becomes uniform, and the outer periphery of the first rubber-like elastic body 38 is When assembling the second rubber-like elastic body 40 or fixing a bearing bracket (not shown) on which the insulator holder 30 is mounted to the vehicle body panel side, it is necessary to perform these operations while checking the position of the overlapping portion 42. As a result, the assembly workability can be greatly improved over the conventional one. In addition, since the rigidity of the overlapping portion 42 can be maintained at the rigidity of the design of the second rubber-like elastic body 40, the desired ability of the second rubber-like elastic body 40 can be completely achieved. Therefore, it is possible to minimize the influence of vibrations from the propulsion shafts 13 and 33 side.

In the present embodiment, the width dimension of the overlapping portion 42 and the width dimension of the portion other than the overlapping portion 42 are clearly separated, but the base end portion of the overlapping portion 42 and this overlapping portion are overlapped with each other. In order to avoid stress concentration in the connecting portion 44 with the portion other than the portion 42, it is also effective to form the connecting portion 44 in a tapered shape whose width dimension changes continuously.

As described above, in this embodiment, by setting the width of the overlapping portion 42 to be small, the second rubber-like elasticity in the direction perpendicular to the axis of the connecting shaft portion 25 of the first propulsion shaft 13 is obtained. Although the rigidity of the body 40 is set to be uniform, a thinned portion is formed in the overlapping portion 42 so that it can be oriented in a direction perpendicular to the axis of the connecting shaft portion 25 of the first propulsion shaft 13. It is also possible to set the rigidity of the second rubber-like elastic body 40 to be uniform.

FIG. 5 shows the sectional structure of the second rubber-like elastic body in one embodiment of the intermediate bearing device according to the second mode of the present invention, and FIG. 6 shows its expanded shape. That is, the overlapping portions 46 are formed on both ends of the second rubber-like elastic material 45 in the form of a strip, and these overlapping portions 46 are connected to each other via the adhesive layer 47 made of an adhesive. Thereby, the second rubber-like elastic body 48 is formed. In the overlapping portion 46 of the second rubber-like elastic body 48, two cavities 49 arranged in the width direction are formed along the longitudinal direction of the elastic body material 45, respectively. The cross-sectional shape and the like of these cavities 49 functioning as the openings are set so that the rigidity of the portion of the overlapping portion 42 is equal to the rigidity of the portion other than this overlapping portion 42.

As a result, the rigidity of the second rubber-like elastic body 48 in the direction perpendicular to the axis of the connecting shaft portion 25 of the first propulsion shaft 13 becomes uniform, and the outer periphery of the first rubber-like elastic body 38 is When assembling the second rubber-like elastic body 48 or fixing a bearing bracket (not shown) on which the insulator holder 30 is mounted to the vehicle body panel side, it is necessary to perform these operations while checking the position of the overlapping portion 46. As a result, the assembly workability can be greatly improved over the conventional one. In addition, since the rigidity of the overlapping portion 46 can be maintained at the rigidity when the second rubber-like elastic body 48 is designed, the desired ability of the second rubber-like elastic body 48 can be completely achieved. Therefore, it is possible to minimize the influence of vibrations from the propulsion shafts 13 and 33 side.

In this embodiment, the cavities 49 are formed as the lightening portions in the overlapping portions 46, but it is possible to form the cavities 49 only in either one of the overlapping portions 46, and further, in the overlapping portion 46. The same effect can be obtained by forming a lightening portion that penetrates in the width direction.

By the way, an example of the relationship between the elastic displacement amount of the second rubber-like elastic body 48 in the direction perpendicular to the axis of the connecting shaft portion 25 and the spring constant of the second rubber-like elastic body 48 will be described. As shown in FIG. 7, it is also possible to use a second rubber-like elastic body having different rigidity depending on the amount of displacement in the vertical direction and the amount of displacement in the horizontal direction perpendicular to the axis of the connecting shaft portion 25.

The external appearance of the second rubber-like elastic body in one embodiment of the intermediate bearing device according to the third mode of the present invention is shown in FIG. 8 and its developed shape is shown in FIG. That is, the overlapping portions 51 are formed at both ends of the second rubber-like elastic material 50 in the form of a strip, and these overlapping portions 51 are mutually connected via the adhesive layer 52 made of an adhesive. The second rubber-like elastic body 53 is formed by joining. The width dimension of the overlapping portion 51 of the second rubber-like elastic body 53 is set to be smaller than the width dimension of the portion other than the overlapping portion 51. In this embodiment, the overlapping portion 51 is a vertical portion of the vehicle body. The bearing bracket and the rotating shaft (not shown) are positioned so as to be located on the upper side in the direction.

A thin portion 54 is cut out in the inner periphery of the above-mentioned overlapping portion 51 and in the inner periphery on the lower end side of the second rubber-like elastic body 53 facing the overlapping portion 51 at an angle of 180 degrees. The width dimension of the overlapping portion 51 located on the upper end side of the second rubber-like elastic body 53 is such that the rigidity of this overlapping portion 51 is formed on the lower end side of the second rubber-like elastic body 53. The rigidity is set to be equal to the rigidity of the thin portion 54.

As a result, the rigidity of the second rubber-like elastic body 53 in the vertical direction perpendicular to the axis of the rotating shaft (not shown) is higher than the rigidity of the second rubber-like elastic body 53 in the lateral direction perpendicular to the vertical direction. It is possible to provide the intermediate bearing device which is small in size and has the second rubber-like elastic body 53 having the characteristics shown in FIG. 7.

In this embodiment, as in the case of the previous embodiment, stress concentration at the base end portion of the overlapping portion 51 and the both end portions of the thin portion 54 where the thickness and width dimensions change rapidly is avoided. Therefore, it is also effective to form these parts in a tapered shape in which the width dimension and the wall thickness continuously change. In addition, in the present embodiment, the thin rubber portion 53 is formed by cutting out a part of the inner circumference of the second rubber-like elastic body 53, so that the vertical direction and the horizontal direction perpendicular to the axis of the rotating shaft are horizontal. Although the rigidity of the second rubber-like elastic body 53 is changed, the same effect can be obtained by changing the dimension of the second rubber-like elastic body 53 in the width direction (direction parallel to the axis of the rotating shaft). It is also possible.

The external appearance of the second rubber-like elastic body in another embodiment of the intermediate bearing device according to the third mode of the present invention is shown in FIG. 10, and its developed shape is shown in FIG. That is, the overlapping portions 56 are formed at both ends of the second rubber-like elastic material 55 having a strip shape, and these overlapping portions 56 are joined to each other via the adhesive layer 57 made of an adhesive. As a result, the second rubber-like elastic body 58 is formed. High-rigidity portions 59 and low-rigidity portions 60 are formed on both end surfaces of the second rubber-like elastic body 58 alternately in four pairs along the circumferential direction of the second rubber-like elastic body 58. The low-rigidity portion 60 in the example is formed by notching both end surfaces of the second rubber-like elastic body 58 to reduce the width dimension thereof.

The width dimension of the superposed portion 56 to be the high-rigidity portion 59 is set to be equal to the rigidity of the other high-rigidity portion 59, but the high-rigidity portion 59 and the low-rigidity portion 60 are It is possible to make the superposed portion 56 the low-rigidity portion 60 depending on the number of divisions of the sub-parts. In this case, the width dimension of the superposed portion 56 is set to be equal to the rigidity of the other low-rigidity portion 60. Not to mention the need.

In this embodiment, similarly to the previous embodiment shown in FIGS. 1 to 4, stress concentration is avoided at the connecting portion between the high-rigidity portion 59 and the low-rigidity portion 60 where the width dimension changes abruptly. Therefore, it is also effective to form the connecting portions in a tapered shape in which the width dimension changes continuously. Further, in this embodiment, four sets of high-rigidity portions 59 and four sets of low-rigidity portions 60 are formed, but two sets of high-rigidity portions and high-rigidity portions are formed as in the previous embodiment shown in FIGS. 8 and 9. It is also possible to set the region of 59 and the region of the low rigidity portion 60 at unequal intervals as needed. Further, in the third mode of the present invention according to FIGS. 8 to 11, a combination of the first mode of the present invention has been described, but the second mode of the present invention shown in FIGS. It is naturally possible to appropriately combine the third aspect of the present invention.

[0045]

[Effect of device]

 According to the intermediate bearing device of the present invention, the width dimension of the overlapping portion of one rubber-like elastic body is set smaller than the width dimension of the other portion, or the lightening portion is formed in the overlapping portion. , The spring constant of one rubber-like elastic body in the direction perpendicular to the axis of the rotating shaft has been made uniform so that the overlapping portion can be used when assembling this one rubber-like elastic body. It is no longer necessary to perform work while checking the position of, and assembly workability can be greatly improved over the conventional one. Also, since the overlapping part can be made to match the spring constant when designing one rubber-like elastic body, it is possible to fully demonstrate the original desired performance of the insulator, and the rotating shaft side. The effect of vibration from can be minimized.

On the other hand, since the notch along the circumferential direction is formed in one of the two rubber-like elastic bodies, an insulator having different rigidity is provided as needed in the direction of an arbitrary load. It is possible to provide an intermediate bearing device.

[Brief description of drawings]

FIG. 1 is a cutaway view of an embodiment in which an intermediate bearing device according to the present invention is applied to a propulsion shaft portion of a vehicle.

FIG. 2 is an extracted enlarged sectional view of a portion of the intermediate bearing device.

FIG. 3 is a perspective view showing an appearance of a portion of the second rubber-like elastic body.

FIG. 4 is a perspective view showing a developed state of the second rubber-like elastic body shown in FIG.

FIG. 5 is a sectional view showing the structure of a second rubber-like elastic body in another embodiment of the intermediate bearing device according to the present invention.

6 is a perspective view showing a developed state of the second rubber-like elastic body shown in FIG.

FIG. 7 is a graph schematically showing the relationship between the elastic displacement of the second rubber-like elastic body and the spring constant of the second rubber-like elastic body.

8 is a perspective view showing the appearance of a second rubber-like elastic body of the intermediate bearing device according to the present invention which satisfies the characteristics shown in FIG. 7. FIG.

9 is a perspective view showing a developed state of the second rubber-like elastic body shown in FIG.

FIG. 10 is a perspective view showing the appearance of a second rubber-like elastic body in another embodiment of the intermediate bearing device according to the present invention.

11 is a perspective view showing a developed state of the second rubber-like elastic body shown in FIG.

FIG. 12 is a sectional view showing an example of a conventional intermediate bearing device.

FIG. 13 is a perspective view showing an appearance of the second rubber-like elastic body.

FIG. 14 is a perspective view showing a developed state of the second rubber-like elastic body.

[Explanation of symbols]

 25 connection shaft part 28 intermediate bearing 29 insulator 38 first rubber-like elastic body 40 second rubber-like elastic body 41 second rubber-like elastic material 42 superposed portion 45 second rubber-like elastic material 46 superposition Part 48 Second rubber-like elastic body 49 Cavity 50 Second rubber-like elastic body material 51 Lap portion 53 Second rubber-like elastic body 54 Thin portion 55 Second rubber-like elastic material 56 Lap portion 58 Second rubber-like elastic body 60 Low rigidity part

 ─────────────────────────────────────────────────── ─── Continuation of the front page (72) Inventor Yasuo Katagiri 1370, Onna, Atsugi, Kanagawa

Claims (3)

[Scope of utility model registration request] 1. An insulator, which is provided on the outer peripheral side of an intermediate bearing attached to a rotating shaft, and which is made of two annular rubber-like elastic bodies, wherein one of the rubber-like elastic bodies is a strip-shaped material. An intermediate bearing device formed in an annular shape by joining overlapping portions formed at both ends to each other, wherein a width dimension of the overlapping portion is smaller than a width dimension of a portion other than the overlapping portion. An intermediate bearing device characterized by being a thing. 2. An insulator comprising two annular rubber-like elastic bodies provided on the outer peripheral side of an intermediate bearing attached to a rotary shaft, wherein one of the rubber-like elastic bodies is a strip-shaped material. An intermediate bearing device formed in an annular shape by joining overlapping portions formed on both end portions to each other, wherein the overlapping portion is formed with a thinned portion. apparatus. 3. An insulator comprising two annular rubber-like elastic bodies provided on the outer peripheral side of an intermediate bearing attached to a rotary shaft, wherein one of the rubber-like elastic bodies extends in the circumferential direction. An intermediate bearing device having a cutout formed therein.