JPH0412256Y2 - - Google Patents

Description

[Detailed Description of the Invention] [Industrial Application Field] The present invention relates to a bearing in which rolling elements are interposed between an outer race and an inner race.

[Conventional technology]

FIG. 3 shows a crank press, and in the figure, reference numeral 11 indicates a crankshaft disposed in the crown portion 15 of the press machine 13. As shown in FIG.

This crankshaft 11 has a flywheel 1
9, a clutch 21 and a brake 23 are arranged.

Rotation of a motor 25 is transmitted to the crankshaft 11 via a drive mechanism (not shown).

The crankshaft 11 is supported by a plurality of bearings 27, and one end of a connecting rod 31 is connected to the crank portion 29 of the crankshaft 11.
A slide 33 of the press machine 13 is connected to the other end of the connecting rod 31.

A bolster 37 is disposed below the slide 33 and supported by a bed 35.

In the crank press configured as above,
As the crankshaft 11 rotates, the connecting rod 31 moves up and down, and the slide 33 moves up and down.
is moved up and down along the column 39, and the slide 33
is fitted into the bolster 37, and press working is performed.

[Problem that the invention attempts to solve]

In such a crank press, a large load is instantaneously applied to the slide 33 during press working, that is, when the slide 33 is fitted to the bolster 37. A high load will also temporarily act on the bearing 27 portion.

4 and 5 show a conventional bearing 27, in which an outer race 41
A rolling element 45 is interposed between the inner race 43 and the inner race 43, and the crankshaft 11 to be supported is inserted through the inner race 43. In addition, the rolling element 4
5 is supported by a retainer 47.

In this bearing 27, the amount of deformation due to the operating load rating of the rolling elements 45 in consideration of a predetermined life is δ1, the amount of deformation due to the static load rating, which is the limit load at which plastic deformation occurs in the rolling elements 45, is δ2, and the amount of deformation due to the static load rating, which is the limit load at which plastic deformation occurs in the rolling elements 45, is δ2. Moving object 4
5 and the outer race 41 is defined as δ3.

When a high load is temporarily applied to such a bearing 27, a load higher than the static load rating acts on the rolling elements 45, plastic deformation occurs in the rolling elements 45, and the rolling elements against the inner race 43 and outer race 41 are There is a possibility that plastic deformation may occur on the raceway surfaces 48 and 49 of the 45.

Therefore, conventionally, in order to prevent plastic deformation of the raceway surfaces 48, 49 and rolling elements 45 of the bearing 27 due to this temporary high load, it has been necessary to increase the size and number of the bearing 27.

[Purpose of invention]

The present invention solves the above problems and provides a bearing that, despite its small size, can reliably prevent plastic deformation of the bearing raceway and rolling elements due to temporary high loads. The purpose is to

[Means for solving problems]

The bearing according to the present invention has an annular outer race that protrudes from both sides of an annular sliding bearing part, and an annular inner race that is arranged inside these outer races via rolling elements. The dimension C obtained by subtracting the inner radius of the inner race from the inner radius of the plain bearing is:
When the amount of deformation due to the operating load rating of the rolling element is δ1, the amount of deformation due to the static load rating is δ2, and the gap dimension formed between the rolling element and the outer race when no load is applied is δ3, δ1+δ3<C The dimensions are <δ2+δ3.

[Effect of invention]

In the present invention, an annular outer race is formed by protruding from both sides of an annular sliding bearing part, and an annular inner race is arranged inside these outer races via rolling elements, and further, Dimension C is calculated by subtracting the inner radius of the inner race from the inner radius of the sliding bearing, δ1 is the amount of deformation due to the operating load rating of the rolling element, δ2 is the amount of deformation due to the static load rating, and the distance between the rolling element and the outer race when no load is applied. When the dimension of the gap formed between the
When such a temporary high load is applied, the sliding bearing comes into contact with the shaft inserted into the inner race of the bearing, and this contact causes the sliding bearing to support the load, causing the bearing raceway surface and It becomes possible to reliably prevent plastic deformation of the rolling elements.

On the other hand, during normal loading, the deformation of the bearing is
is less than δ2+δ3, the sliding bearing part does not come into contact with the shaft inserted through the bearing, and the load is supported by the rolling elements and the bearing rotates smoothly.

[Example of idea]

Hereinafter, details of the present invention will be described with reference to an embodiment shown in the drawings.

1 and 2 show an embodiment of the bearing of the present invention, and in these figures, reference numeral 51
1 shows an annular sliding bearing portion, and on the inner surface of this sliding bearing portion 51, a metal portion 52 made of, for example, a bronze bearing alloy is formed. An annular outer race 55 is formed integrally with the slide bearing 51 so as to protrude from both sides of the slide bearing 51 .

Inner laces 53 are arranged inside these outer laces 55 at regular intervals.

Inner lace 53 and outer lace 55
are formed with arcuate raceway surfaces 57 and 59, and between these raceway surfaces 57 and 59 are rolling elements 6.
1 is arranged rotatably. In addition, the rolling element 6
1 is supported by a retainer 63.

In addition, in this bearing, the amount of deformation due to the operating load rating of the rolling elements 61 considering the predetermined life is δ1, the amount of deformation due to the static load rating, which is the limit load at which plastic deformation occurs in the rolling elements 61, is δ2, and the amount of deformation when no load is applied is δ2. The dimension of the gap formed between the rolling element 61 and the outer race 55 is δ3.

Therefore, in the bearing of this embodiment, the inner radius of the metal portion 57 of the sliding bearing portion 51 is larger than the inner radius of the inner race 53 by a minute dimension C.

This minute dimension C is set to a dimension that satisfies δ1+δ3<C<δ2+δ3 with respect to δ1, δ2, and δ3 described above.

In the bearing configured as described above, the annular outer race 55 is formed by protruding from both side surfaces of the annular sliding bearing portion 51, and the annular outer race 55 is formed inside the outer race 55 via the rolling elements 61. An inner lace 53 is arranged, and further,
Dimension C obtained by subtracting the inner radius of the inner race 53 from the inner radius of the metal part 52 of the sliding bearing part 51
When the amount of deformation due to the operating load rating of the rolling element 61 is δ1, the amount of deformation due to the static load rating is δ2, and the gap dimension formed between the rolling element 61 and the outer race 55 when no load is applied is δ3, Since the dimensions were set such that δ1 + δ3 < C < δ2 + δ3, the deformation of the bearing is δ2 + δ3.
When the above temporary high load acts, the metal part 52 of the sliding bearing part 51 comes into contact with, for example, the crankshaft 65, and this contact causes the sliding bearing part 5
1 supports the load, making it possible to reliably prevent plastic deformation of the raceway surfaces 57, 59 of the bearing and the rolling elements 61.

As a result, it becomes possible to easily support a high load with a smaller bearing than before.

On the other hand, during normal loading, the deformation of the bearing is
is less than δ2+δ3, the metal portion 52 of the sliding bearing portion 51 does not come into contact with the crankshaft 65, the load is supported by the rolling elements 61, and the bearing rotates smoothly.

In the embodiments described above, the present invention was applied to radial ball bearings, but the present invention is not limited to such embodiments. For example, the present invention is applicable to roller bearings, taper bearings, needle bearings, etc. Needless to say, the present invention can be applied to other types of bearings, as well as thrust bearings.

[Effect of idea]

As described above, according to the present invention, an annular outer race is formed by protruding from both sides of an annular sliding bearing part, and an annular inner race is formed inside these outer races via rolling elements. Furthermore, the dimension C obtained by subtracting the inner radius of the inner race from the inner radius of the plain bearing is δ1, the amount of deformation due to the rated load of the rolling element, δ2 is the amount of deformation due to the static rated load, and the amount of deformation due to the rated static load is δ2. The gap dimension formed between the outer race and the outer race is δ3
Since the dimensions are set such that δ1+δ3<C<δ2+δ3, it is possible to reliably prevent plastic deformation of the raceway surface of the bearing and the rolling elements.

[Brief explanation of the drawing]

Fig. 1 is a longitudinal sectional view showing an embodiment of the bearing of the present invention, Fig. 2 is an enlarged longitudinal sectional view showing the main parts of Fig. 1, and Fig. 3 is a longitudinal sectional view showing a press machine. FIG. 4 is a vertical cross-sectional view showing a conventional bearing, and FIG. 5 is a vertical cross-sectional view showing a part of the bearing shown in FIG. 4 in an enlarged manner. 51... Sliding bearing portion, 53... Inner race, 55... Outer race, 61... Rolling element.

Claims (1)

[Claims for Utility Model Registration] An annular outer race is formed by protruding from both sides of an annular sliding bearing part, and an annular inner race is arranged inside these outer races via rolling elements. The dimension C obtained by subtracting the inner radius of the inner race from the inner radius of the sliding bearing is δ1, the amount of deformation due to the rated load of the rolling element is δ1, the amount of deformation due to the static load rating is δ2, and the amount of deformation due to the static load rating is δ2. A bearing characterized in that, where δ3 is a gap formed between a rolling element and an outer race, δ1+δ3<C<δ2+δ3.