JP2005195181A - Pin-like holder - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a pin-like holder capable of applying high-precision processing to a fitted portion between a head section of a pin and a side plate fitted thereto and capable of improving the strength of the pin without need for increasing the thickness of the pin itself. <P>SOLUTION: This pin-like holder, having such a structure as to support the pin 12 passing through a pin hole 4a of a hollow roller 4, engages a hollow roller 4 with the side plate 13 through an engaging projection T larger than the pin 12 in diameter. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

  The present invention relates to an improvement of a pin-type cage of a rolling bearing, and in particular, a pin breakage in a bearing used in a facility that generates a large vibration such as a rolling mill, a reduction gear for a rolling mill, a pinion stand, and a crusher. The present invention relates to a pin-type cage suitable for prevention.

  An example of a conventional pin cage is disclosed in Japanese Utility Model Laid-Open No. 60-182525. As shown in FIG. 4, the conventional pin-type cage 1 is composed of a pin 2 and side plates 3 and 3 that support both ends thereof. The pin 2 passes through the pin hole 4 a in the axial center portion of the hollow roller 4. An end (pin head) 2a of the pin 2 supported by one side plate 3 has a large diameter, and is fitted into a through hole 3a formed in the side plate 3 and fixed by welding. Stops and comes off. The end portion 2 b supported by the other side plate 3 is screwed to the side plate 3 with a taper screw 5.

  However, in the case of the conventional pin-type cage 1 disclosed in the above publication, since there is a gap C between the outer diameter of the pin head 2a on the welding side and the inner diameter of the through hole 3a of the side plate 3, When the roller 4 collides with or presses against the pin 2 during the operation of the pin 2 and a force acts on the pin 2, the durability of the welded portion having a low strength becomes a problem. In order to remedy this drawback, the gap C between the pin head 2a and the through hole 4a of the side plate must be eliminated, and the processing accuracy must be strictly controlled, resulting in high costs.

  On the other hand, a proposal for eliminating or minimizing the gap C between the welding-side pin head 2a and the side plate through-hole 3a without precision machining is disclosed in, for example, Japanese Utility Model Publication No. 53-41642 (FIG. No. 5), No. 50-150656 (see FIG. 6), No. 6-13380 (see FIG. 7), No. 1-18891 (see FIG. 8), and the like. However, in these other conventional pin-type cages 1, the strength of the pin 2 itself is improved even if the fitting clearance between the pin head 2 a on the welding side and the through hole of the side plate 3 is eliminated. Is not considered. That is, since the diameter of the pin hole 4a penetrating the shaft center portion is restricted from the point of strength of the hollow roller 4 held by the pin type cage 1, the diameter of the pin 2 is inevitably restricted, There is a problem that it is difficult to increase the strength by increasing the thickness of the pin 2.

  Therefore, the present invention has been made paying attention to the problems of such a conventional pin-type cage, and has been subjected to precision machining to eliminate the gap between the pin head and the side plate to which it is fitted. An object of the present invention is to provide a pin-type cage capable of improving the strength without making the pin itself thick.

  In order to achieve the above object, the present invention according to claim 1 is a pin-type cage having a structure in which a pin penetrating a pin hole of a hollow roller is supported by a side plate, and the hollow roller and the side plate are connected to each other by a pin. The engagement is made through an engagement protrusion having a large diameter.

As described above, according to the present invention, the acting force from the hollow roller is received through the engaging protrusion having a diameter larger than that of the pin and is not directly applied to the pin itself or the welded portion of the pin and the side plate. Therefore, breakage of the pins and breakage of the welded portion can be effectively prevented.
Moreover, it is not necessary to make the pin itself complicated or to have a large cross-sectional area, and it is not necessary to strictly manage the processing accuracy, so that the cost is low.

Hereinafter, embodiments of the present invention will be described with reference to the drawings. In addition, in each figure, the same code | symbol is attached | subjected to the same or an equivalent part, and the overlapping description is abbreviate | omitted.
FIG. 1 is a cross-sectional view of a main part of a cylindrical roller bearing equipped with a pin-shaped cage 10A of the present invention showing a first embodiment. First, the configuration of the pin-type cage 10A will be described. The pin-shaped cage 10A includes a pin 12 that rotatably holds a plurality of hollow rollers 4 that are equally arranged between the outer ring 11g and the inner ring 11n, and this pin. The side plates 13, 13 that support both ends of the pin 12, and the bushes 14 that are interposed between the pins 12 and the side plate 13 and that form engaging protrusions having a larger cross-sectional area than the pins 12.

The pin 12 has a uniform thickness and penetrates the pin hole 4a in the axial center portion of the hollow roller 4 with a gap H maintained.
The side plate 13 has an annular shape and is disposed in an annular gap space formed between the end of the outer ring 11g of the roller bearing and the end of the inner ring 11n. On the annular plane of the side plate 13, a plurality of through holes that engage with the bushes 14 fixed to both ends of the pin 12 are arranged as bush engaging holes 13a at equal intervals on the circumference. The inner plane 13b of the side plate faces the end face 4b of the hollow roller 4 and functions as a roller guide surface.

  The bush 14 includes a cylindrical portion 14a having a diameter larger than that of the pin 12 and a flange portion 14f provided at the rear end thereof, and has a pin engaging hole 14c penetrating the shaft center of both portions. The outer diameter surface of the cylindrical portion 14a is fitted into the bushing engagement hole 13a of the side plate 13 with a tightening margin. Further, the stepped flat surface 14b of the flange portion 14f hits the side plate 13 and is positioned in the axial direction. The bushes 14 thus coupled to the side plates 13 are fixed together by welding 15. The pin 12 is fitted into the bush 14 through the pin engaging hole 14c, and the pin end portion and the bush 14 are fixed by welding 16 to be integrated.

The tip of the cylindrical portion 14 a of the bush 14 integrated with the holding pin 12 and the side plate 13 protrudes inward from the inner plane 13 b of the side plate 13 to form an engagement protrusion T having a diameter larger than that of the pin 12. . The engagement protrusion T is loosely engaged with a counterbore (bush engagement hole) 4 c provided concentrically with the pin hole 4 a on the end surface of the hollow roller 4.
Here, the interrelationship between the engagement gaps between the hollow roller 4 and the integrated pin 12, side plate 13, and bush 14 will be described.

First, the axial clearance will be described. The opposing gap δ between the inner flat surface 13b of the side plate 13 and the end surface 4b of the hollow roller 4, the end surface 14d of the cylindrical portion 14a of the bush, and the end surface 4d of the roller counterbore hole (bush engagement hole) facing this. Is set to δ <Δ.
Next, the radial clearance will be described. The outer diameter surface of the engagement protrusion T at the tip of the cylindrical portion 14a of the bush 14 and the inner diameter surface of the roller counterbore hole (bush engagement hole) 4c opposed thereto. And the radial clearance H between the outer diameter surface of the pin 12 and the inner diameter surface of the pin hole 4a of the hollow roller 4 opposed thereto is set to h <H. It is.

Subsequently, the operation will be described.
The hollow roller 4 held by the pin-shaped cage 10A is not guided by the outer diameter surface of the pin 12 as in the prior art, but the tip of the cylindrical portion of the bushing 14 having a diameter larger than that of the pin 12, that is, the engagement protrusion. Guided by part T. The outer diameter of the engagement protrusion T at the tip of the bush 14 is larger than the radial gap H between the outer diameter surface of the pin 12 passing through the pin hole 4a of the hollow roller 4 and the inner diameter surface of the pin hole 4a. Since the clearance h in the radial direction between the surface and the inner diameter surface of the roller counterbore hole (bushing engagement hole) 4c facing the surface is set to be smaller (h <H), the hollow roller 4 Is brought into contact with and guided by the engaging protrusion T at the tip of the bush before contacting the pin 12. Therefore, the force acting from the hollow roller 4 is received by the cylindrical portion 14a of the bush having a large diameter, and is not received by the pin 12 having a small cross-sectional area.

Further, the side plate 13 is in close contact with the bush 14 at the stepped portion plane 14b, and both the portions 13 and 14 are joined with no gap in the axial direction. Moreover, the axial clearance δ between the end surface 4b of the hollow roller and the inner flat surface 13b of the side plate 13 is the counterbore (bush engagement hole) 4c of the hollow roller facing the tip surface 14d of the bush 14. It is set smaller than the axial gap Δ between the end face 4d (δ <Δ). Therefore, even when the pin-shaped cage 10 </ b> A moves in the axial direction and collides with the end surface 4 b of the hollow roller 4, the collision force is received by the bush stepped plane 14 b via the side plate 13. Therefore, no force acts directly on the welded portions 15 and 16 fixing the side plate 13 and the bush 14.
Thus, according to this embodiment, instead of receiving the force applied from the hollow roller 4 with the pin 12 having relatively low strength, the pin 12 itself is damaged or welded by receiving the bushing 14 with high strength. Breakage of the portions 15 and 16 can be reliably prevented.

  FIG. 2 is a cross-sectional view of a main part of a cylindrical roller bearing equipped with the pin-shaped cage 10B of the present invention showing the second embodiment. This pin type cage 10B is different from the first embodiment in the shape of the bush and how to attach it to the side plate 13. That is, the bush 24 is cylindrical and has no flange portion. Then, the bush 24 is fitted into the counterbore hole 21 provided on the inner flat surface 13b facing the end face 4b of the hollow roller 4 of the side plate 13 by a method such as press-fitting or driving in at one end of the cylindrical shape. The side plate 13 is fixed integrally. The other end side of the bush 24 protrudes from the inner plane 13 b of the side plate 13 to form a cylindrical engagement protrusion T having a diameter larger than that of the pin 12. The pin-shaped cage 10B is formed by inserting the pin 12 into pin engagement holes 24c and 13c penetrating through the bush 24 and the axis of the side plate 13 and fixing the end of the pin to the side plate 13 by welding 16. .

  The engagement protrusion T is loosely engaged with a counterbore (bush engagement hole) 4c provided concentrically with the pin hole 4a on the end face 4b of the hollow roller 4 via a radial gap h. This is the same as that shown in FIG. Also in this case, the radial gap h is smaller than the radial gap H between the pin hole 4a of the hollow roller 4 and the pin 12. Thereby, the force acting from the hollow roller 4 is received by the bush 24 having a large diameter, and the pin 12 having a small cross-sectional area is prevented from being damaged. Further, the axial gap δ between the hollow roller 4 and the side plate 13 is made smaller than the axial gap Δ between the end face 4d of the counterbore 4c of the hollow roller and the bush 24a, so that the pin type cage The collision force between 10B and the hollow roller 4 is received by the side plate 13 to prevent the force from directly acting on the welded portion 16 between the pin 12 and the side plate 13.

FIG. 3 is a cross-sectional view of a main part of a cylindrical roller bearing equipped with a pin type cage 10C of the present invention showing a third embodiment.
In the case of this pin-shaped cage 10C, a bush is not used, and a cylindrical engagement protrusion T that protrudes in the axial direction with an outer diameter larger than that of the pin 12 is provided on the end face of the hollow roller 4, and the side plate 13 The point which comprised the counterbore 31 which the said engaging protrusion T fits in and comprised is different from said each embodiment. The counterbore 31 provided on the inner flat surface 13 b of the side plate 13 is concentric with the protrusion T of the hollow roller 4. The counterbore 31 has a radial gap h and an axial gap δ, and the engagement protrusion T of the hollow roller 4 is fitted. The side plate 13 is provided with a pin engaging hole 13c concentrically with the counterbore hole 31. After passing the pin 12 through the pin engaging hole 13c and the pin hole 4a of the hollow roller 4, both ends of the pin 12 are welded. The pin-shaped cage 10C is formed by being fixed to the side plate 13 by 16.

The radial gap h between the outer diameter surface of the engaging projection T projecting from the end of the hollow roller 4 and the inner diameter surface of the counterbore 31 is between the outer diameter surface of the pin 12 and the hollow roller 4. It is smaller than the radial clearance H between the inner surface of the pin hole 4a. Therefore, the hollow roller 4 is guided by the engaging protrusions T projected from both end faces of the hollow roller 4, and the force acting on the hollow rollers 4 is received by the side plate 13 through the engaging protrusions T. Since no force acts directly on the pin 12 itself or the welded portion 16 at the end of the pin, damage to the pin 12 itself or to the welded portion 16 can be prevented.
In each of the above embodiments, a cylindrical roller bearing has been described as an example of a rolling bearing to which the pin cage of the present invention is applied. However, the present invention is not limited to this, and the present invention is not limited to a tapered roller bearing or a self-aligning roller bearing. The pin-type cage can be suitably applied, and the same effect as in the case of the cylindrical roller bearing can be obtained.

It is sectional drawing of 1st Embodiment of the pin type holder | retainer of this invention. It is sectional drawing of 2nd Embodiment of the pin type holder | retainer of this invention. It is sectional drawing of 3rd Embodiment of the pin type holder | retainer of this invention. It is sectional drawing of the conventional pin-shaped cage. It is sectional drawing of the other conventional pin-shaped cage. It is sectional drawing of the other conventional pin-shaped cage. It is sectional drawing of the other conventional pin-shaped cage. It is sectional drawing of the other conventional pin-shaped cage.

Explanation of symbols

2 pin 4 hollow roller 4a pin hole 10A pin type cage 10B pin type cage 10C pin type cage 12 pin 13 side plate T engaging protrusion

Claims (1)

  A pin-type cage having a structure in which a pin penetrating a pin hole of a hollow roller is supported by a side plate, wherein the hollow roller and the side plate are engaged via an engagement protrusion having a diameter larger than that of the pin. Pin type cage.

Images