JP3009619B2 - Elastic support bearing - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a bearing for a mechanical device, such as a turbine device bearing, which rotates at high speed, has small mechanical loss, and has a small bearing space.

[0002]

2. Description of the Related Art Conventionally, elastic support bearings and damper bearings using ball bearings are rarely used for bearings having a large radial load or a small radial load. One that has been used or one that supports the axial load by another mechanism has been used.

[0003] A conventional device employing an axial load will be described with reference to FIG. A bearing 10 is fitted into the sleeve 1, and a pair of “O” rings 3 are incorporated between the sleeve 1 and the support flange 8 so as to be spaced apart in the axial direction. The “O” ring 3 has a role of sealing oil for an oil damper and receives a radial load. The support flange 8 bears a load applied from the “O” ring 3.

The support flange 8 is attached to the main body casing 5 with bolts 11. A thrust flange 9 that receives an axial load from a shaft is attached to the support flange 8.

The thrust flange 9 receives an axial load. The cylindrical portion 9a is thinned so that it does not act much on the radial load, so that it is soft in the radial direction and rigid in the thrust direction. ing.

[0006]

However, the above-described device is very difficult to realize, and troubles such as fatigue damage of the cylindrical portion 9a of the thrust flange 9 are likely to occur. In addition, the mounting dimensions of the entire bearing portion are increased, and the cost is increased.

[0007] When the size of the main body device is reduced or increased outside a certain range, the bearing device side must also be reduced in size or increased in size. There is a limit to making the support flange 8 and the thrust flange 9 more compact than necessary.

Further, it is desired to reduce the distance between the shafts to shorten the shaft length, thereby reducing the shaft diameter to reduce the overall cost, or to solve the vibration problem and to cope with a higher speed. There are many things.

An object of the present invention is to solve and solve these problems and to provide a better bearing device.

[0010]

SUMMARY OF THE INVENTION The present invention has been made to solve the above-mentioned problems, and has an axially spaced pair of "O" rings attached to the outer periphery of a bearing sleeve fixed to an outer ring of a bearing. In a bearing in which a load and a radial load are applied, a half-split ribbon is disposed in the lower half of the outer periphery of the bearing sleeve between the pair of “O” rings, and a space extending in the axial direction is formed in a solid portion of the bearing sleeve. An elastic support bearing is provided, wherein the sleeve is fixed to a fixing flange by a thrust bolt penetrating the space.

That is, one end of a thrust bolt is attached to a sleeve fixed to the bearing so as to make the bearing structure compact, and the other end of the thrust bolt is attached to a fixed flange to support an axial load from a shaft, and As a structure to escape load, on the other hand, as a structure to support the radial load, a half-ribbon is appropriately incorporated according to the radial load, and further, for example, the inner cylinder is directly attached to the main body casing, so that it is possible to significantly reduce the size. It is like that.

[0012]

DESCRIPTION OF THE PREFERRED EMBODIMENTS One embodiment of the present invention will be described with reference to FIGS. 1 shows a sectional view of a bearing assembly, and FIG. 2 shows an enlarged view of a main part of FIG. Note that the same parts as those of the above-described conventional one are denoted by the same reference numerals in the drawings, and redundant description will be omitted.

The bearing 10 is fixed to the bearing sleeve 1 and a lubrication passage for the bearing is provided therein (not shown), and forced lubrication is performed between the juxtaposed bearings 10. The bearing sleeve 1 is supported by the inner cylinder 2 by a half-split ribbon 6 and an "O" ring 3 to form a gap 2a therebetween.
Is fixed so as not to move in the axial direction by a thrust bolt 4 penetrating a space 1a formed in a solid portion of the bearing sleeve 1.

The thrust bolt 4 is
The oil lubrication pipe 13 has a flexible structure so that it is designed to be displaceable in the radial direction and soft so that the shaft 12, the bearing 10, and the bearing sleeve 1 may be displaced.

The thrust bolt 4 is designed to have a rigidity that does not impede the elastic supporting effect of the "O" ring in the radial load direction, that is, a spring constant one order of magnitude smaller than the spring constant of the "O" ring, and is displaced in the radial direction. Even possible structures, that is, displacement due to the own weight of the shaft, displacement due to disturbance load during rotation, or resonance displacement at the resonance point during rotation, etc.
By allowing displacement in the radial direction, the shaft 12,
The bearing 10 and the bearing sleeve 1 are configured to be integrally displaceable in the radial load direction.

An oil damper is provided between the bearing sleeve 1 and the inner cylinder 2, and "O" rings 3 are inserted on both sides to prevent oil from escaping. In the bearing sleeve 1).

The inner cylinder 2 has a split structure for convenience of disassembly and assembly. Although not shown in the drawing, the inner cylinder 2 is integrally assembled with bolts on a horizontal flange surface and fixed to the main body casing 5. The body casing 5 is provided with one oil damper hole 15.

The number of thrust bolts 4 may be four to eight in accordance with the required axial load. One end is screwed into the bearing sleeve 1 with a screw 4a, and the other end is screwed. The end face 4b of the thrust bolt 4 and the bottom face 7a of the hole of the fixing flange 7 are brought into contact with each other, and are tightened with a nut 14 from the outside so that the bearing 10 is fixed so as not to move in the axial direction. As described above, the thrust bolt 4
Penetrates through the space 1a formed in the bearing sleeve 1,
By being installed within the width of the inner cylinder 2, it can be designed to be small and compact in the width direction.

In this embodiment constructed as described above, when a radial load and a rightward axial load are simultaneously applied to the shaft 12, the radial load is first applied to the half-split ribbon 6.

The number of the half-split ribbons 6 (four in this case), wire diameter,
Considering the crushing allowance and the amount of eccentricity of the axis, it is determined that the condition of the initial radial load such as the dimension of the half-split ribbon groove is met, so that it is supported with a slight displacement due to the radial load.

At this time, even if the half-split ribbon 6 is displaced, the radial load acts on the inner cylinder 2 through the half-split ribbon 6 by providing the gap 2a where the bearing sleeve 1 and the inner cylinder 2 do not come into contact with each other. It is supported by the main body casing 5 fixed to the cylinder 2.

An axial load acting in the right direction is transmitted from the shaft 12 to the bearing 10, and a load is applied to the bearing sleeve 1. The bearing sleeve 1 has a gap 2a with the inner cylinder 2, and also has a gap 7b with the fixed flange 7. The bearing sleeve 1 is fixed at a predetermined axial position with a thrust bolt 4, and the load applied from the bearing sleeve 1 is reduced by the thrust bolt. 4 is supported by tension and compression. Oil is put between a pair of “O” rings 3 and 3 outside the half-split ribbon 6 to form an oil damper mechanism.

As described above, according to the present embodiment, it is possible to achieve a compact bearing that receives a radial load and a thrust load.

Although the present invention has been described with reference to the illustrated embodiment, the present invention is not limited to such an embodiment.
It goes without saying that various changes may be made to the specific structure within the scope of the present invention.

[0025]

As described above, according to the present invention, the bearing structure can be made compact, the overall shaft length can be shortened, the cost can be reduced, and the trouble of vibration problems can be eliminated, and the speed can be further increased. It was done.

[Brief description of the drawings]

FIG. 1 is an assembled sectional view of a bearing according to an embodiment of the present invention.

FIG. 2 is an enlarged view of a main part of FIG.

FIG. 3 is an assembled sectional view of a conventional damper bearing.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Bearing sleeve 2 Inner cylinder 3 "O" ring 4 Thrust bolt 5 Body casing 6 Half-ribbon 7 Fixed flange 10 Bearing 12 shaft

──────────────────────────────────────────────────続 き Continued on the front page (58) Field surveyed (Int. Cl. ⁷ , DB name) F16C 27/04 F16C 27/00

Claims (1)

(57) [Claims] 1. A bearing in which an axial load and a radial load are attached to a pair of "O" rings spaced apart in the axial direction on the outer periphery of a bearing sleeve fixed to an outer ring of the bearing, wherein the pair of "O" rings is A half-split ribbon was provided in the lower half of the outer periphery of the bearing sleeve, a space extending in the axial direction was provided in a solid portion of the bearing sleeve, and the sleeve was fixed to a fixing flange with a thrust bolt penetrating the space. An elastic support bearing characterized by the above.