CN110114586A - Thrust roller bearings and raceway rings for thrust roller bearings - Google Patents

Abstract

A raceway ring (10, 20) for a thrust roller bearing includes raceway surfaces (11, 21), and a plurality of first rollers (30) roll on the raceway surfaces (11, 21). The raceway surfaces (11, 21) have first full-convexities (12, 22) that contact the first roller (30). The shape of the first surface (12s, 22s) of the first full-protrusion (12, 22) in the radial cross section of the raceway ring (10, 20) for a thrust roller bearing is a first single circular arc. Therefore, heat generated by relative sliding of the first rollers (30) with respect to the thrust roller bearing raceway rings (10, 20) can be reduced.

Description

Thrust roller bearings and raceway rings for thrust roller bearings

technical field

The invention relates to a thrust roller bearing and a raceway ring for the thrust roller bearing.

Background technique

There is known a thrust roller bearing provided in a rotating portion of an electrical component such as an automotive transmission, a torque converter, or a compressor of an automotive air conditioner (see Patent Document 1). Thrust roller bearings are used to support thrust loads applied to the above-mentioned rotating parts. The thrust roller bearing described in Patent Document 1 includes: a raceway ring arranged along the direction of the rotation axis; a plurality of rollers rolling on the raceway surface of the raceway ring; Multiple rollers for retention.

prior art literature

patent documents

Patent Document 1: Japanese Patent Laid-Open No. 2003-83333

Contents of the invention

The technical problem to be solved by the invention

However, in the thrust roller bearing disclosed in Patent Document 1, the rollers slide relative to the raceway due to the difference between the peripheral velocity of the rolling surface of the roller and the peripheral velocity of the raceway surface of the raceway. Heat is generated as the rollers slide relative to the raceway. This heat causes peeling at the origin of the surface on the raceway surface of the raceway ring for a thrust roller bearing on which the rollers roll.

The present invention was made in view of the above-mentioned technical problems, and an object of the present invention is to provide a thrust roller bearing and a raceway ring for a thrust roller bearing, which are configured to reduce heat generated by sliding of the rollers relative to the raceway ring.

Technical solutions adopted to solve technical problems

The thrust roller bearing of the present invention comprises: a raceway ring for a first thrust roller bearing; a raceway ring for a second thrust roller bearing; The raceway ring for the bearing and the raceway ring for the second thrust roller bearing are arranged between the raceway ring for the first thrust roller bearing and the raceway ring for the second thrust roller bearing in the circumferential direction. The first raceway ring for a thrust roller bearing and the second raceway ring for a thrust roller bearing each include raceway surfaces on which the first rollers roll. At least one of the raceway surface of the first raceway ring for thrust roller bearing and the raceway surface of the second raceway raceway for thrust roller bearing has a first full convex portion that contacts the first roller. The shape of the first surface of the first full convex portion in the radial section of the thrust roller bearing is a first single arc.

The raceway ring for a thrust roller bearing according to the present invention includes a raceway surface on which a plurality of first rollers roll. The raceway surface has a first full convex portion in contact with the first roller. The shape of the first surface of the first fully convex portion in the radial section of the raceway ring for thrust roller bearing is a first single arc.

Invention effect

The thrust roller bearing of the present invention can reduce the heat generated by the sliding of the first roller with respect to the raceway rings for the thrust roller bearing (the first raceway ring for the thrust roller bearing and the second raceway ring for the thrust roller bearing).

The raceway ring for the thrust roller bearing of the present invention can reduce the occurrence of the first roller sliding relative to the raceway ring for the thrust roller bearing (the raceway ring for the first thrust roller bearing and the raceway ring for the second thrust roller bearing). hot.

Description of drawings

1 is a schematic perspective view of a thrust roller bearing, a first raceway ring for a thrust roller bearing, and a second raceway ring for a thrust roller bearing according to Embodiment 1. FIG.

2 is a schematic cross-sectional view of the first raceway ring for a thrust roller bearing according to Embodiment 1. FIG.

3 is a schematic cross-sectional view of a second raceway ring for a thrust roller bearing according to Embodiment 1. FIG.

4 is a schematic enlarged cross-sectional view of a first roller in Embodiment 1. FIG.

5 is a schematic partial enlarged cross-sectional view of the thrust roller bearing, the first raceway ring for thrust roller bearing, and the second raceway ring for thrust roller bearing according to Embodiment 1. FIG.

6 is a schematic partial enlarged cross-sectional view of the thrust roller bearing, the first raceway ring for thrust roller bearing, and the second raceway ring for thrust roller bearing according to Embodiment 1. FIG.

7 is a diagram showing a graph showing the relationship between the rotational speed and the temperature increase rate of the thrust roller bearings of the working example and Comparative Example 1. FIG.

8 is a diagram showing a graph showing the relationship between the position on the first rolling surface of the first roller and the amount of heat generated per unit length at the position in the thrust roller bearing according to the embodiment.

Fig. 9 shows the position of the first rolling surface of the first roller and the track of the first rolling surface of the first roller and the raceway ring for the first thrust roller bearing in the thrust roller bearing according to the embodiment; Diagram of the relationship between contact surface pressure between surfaces.

10 is a diagram showing a graph showing the relationship between the position on the first rolling surface of the first roller and the amount of heat generated per unit length at the position in the thrust roller bearing of Comparative Example 1. FIG.

11 shows the position of the first rolling surface of the first roller and the first rolling surface of the first roller and the raceway ring for the first thrust roller bearing in the thrust roller bearing of Comparative Example 1. A diagram of a graph of the relationship between the contact surface pressure between the rail surfaces.

12 is a diagram showing a graph showing the relationship between the radius of curvature of the first full convex portion and the center contact surface pressure and the edge contact surface pressure in the thrust roller bearing according to the first embodiment.

13 is a schematic partial enlarged cross-sectional view of a thrust roller bearing, a first raceway ring for a thrust roller bearing, and a second raceway ring for a thrust roller bearing according to Embodiment 2. FIG.

14 is a schematic partial enlarged cross-sectional view of a thrust roller bearing according to a modified example of Embodiment 2, a first raceway ring for a thrust roller bearing, and a second raceway ring for a thrust roller bearing.

15 is a schematic partial enlarged cross-sectional view of a thrust roller bearing, a first raceway ring for a thrust roller bearing, and a second raceway ring for a thrust roller bearing according to Embodiment 3. FIG.

16 is a schematic enlarged cross-sectional view of a first roller according to Embodiment 3. FIG.

17 is a schematic enlarged cross-sectional view of a second roller according to Embodiment 3. FIG.

Detailed ways

Hereinafter, embodiments of the present invention will be described with reference to the drawings. In addition, in the following drawings, the same reference numerals are attached to the same or corresponding parts, and the description thereof will not be repeated.

(Embodiment 1)

The thrust roller bearing 1 and the raceway rings for the thrust roller bearing (the first raceway ring 10 for the thrust roller bearing and the second raceway ring 20 for the thrust roller bearing) according to Embodiment 1 will be described with reference to FIGS. 1 to 6 . The thrust roller bearing 1 mainly includes a raceway ring 10 for a first thrust roller bearing, a raceway ring 20 for a second thrust roller bearing and a plurality of first rollers 30 . The thrust roller bearing 1 may further include a cage 40 that holds the first roller 30 . The first raceway ring 10 for a thrust roller bearing rotates with respect to the second raceway ring 20 for a thrust roller bearing around the rotation shaft 8 via the first roller 30 . In this specification, the inner side is defined as the side close to the rotating shaft 8 , and the outer side is defined as the side away from the rotating shaft 8 . In this specification, the radial direction is defined as a direction perpendicular to the rotation axis 8 .

The raceway ring 10 for the first thrust roller bearing is an annular plate member. The raceway ring 10 for a first thrust roller bearing has a raceway surface 11 on which the first roller 30 rolls, and a first main surface 15 opposite to the raceway surface 11 .

The raceway surface 11 of the first raceway ring 10 for a thrust roller bearing includes the first surface 12s of the first full convex portion 12 of the first raceway ring 10 for a thrust roller bearing. The raceway surface 11 of the first raceway ring 10 for a thrust roller bearing may further include a first outer flat portion 13 and a first inner flat portion 14 . The first outer flat portion 13 may also be provided on the outer side of the first full convex portion 12 . A first inner flat portion 14 may also be provided on the inner side of the first full convex portion 12 .

The first main surface 15 can also be flat. The flat first main surface 15 enables the first raceway ring 10 for a thrust roller bearing to be attached to a housing (not shown) without any gap. Therefore, when a thrust load is applied to the thrust roller bearing 1, the thrust roller bearing 1 can properly withstand the thrust load.

The second raceway ring 20 for a thrust roller bearing is an annular plate member. The raceway ring 20 for the second thrust roller bearing has a raceway surface 21 on which the first roller 30 rolls, and a second main surface 25 on the opposite side to the raceway surface 21 .

The raceway surface 21 of the second raceway ring 20 for a thrust roller bearing includes the first surface 22s of the first full convex portion 22 of the second raceway ring 20 for a thrust roller bearing. The raceway surface 21 of the second raceway ring 20 for a thrust roller bearing may further include a second outer flat portion 23 and a second inner flat portion 24 . A second outer flat portion 23 may also be provided on the outer side of the first full convex portion 22 . A second inner flat portion 24 may also be provided on the inner side of the first full convex portion 22 .

The second main surface 25 can also be flat. The flat second main surface 25 enables the second raceway ring 20 for a thrust roller bearing to be attached to a housing (not shown) without a gap. Therefore, when a thrust load is applied to the thrust roller bearing 1, the thrust roller bearing 1 can properly withstand the thrust load.

In this embodiment, the raceway surface 11 of the first raceway ring 10 for a thrust roller bearing and the raceway surface 21 of the second raceway ring 20 for a thrust roller bearing each have a first fully convex portion 22 . At least one of the raceway surface 11 of the first raceway ring 10 for a thrust roller bearing and the raceway surface 21 of the second raceway ring 20 for a thrust roller bearing may have a first full convex portion on which the first roller 30 contacts. twenty two. It is also possible to provide the first full convex portion on only one of the raceway surface 11 of the raceway ring 10 for the first thrust roller bearing and the raceway surface 21 of the raceway ring 20 for the second thrust roller bearing, while the first full convex portion can be provided on the first thrust roller bearing. The other of the raceway surface 11 of the raceway ring 10 for a bearing and the raceway surface 21 of the second raceway ring 20 for a thrust roller bearing is not provided with the first full convex portion. In this specification, a full convex portion refers to a bulge formed on the raceway surface 11 , 21 . In this specification, the full convex portion refers to the entire rolling surface (first Rolling surface 31) opposite convex portion.

The first fully convex portion 12 of the first raceway ring 10 for a thrust roller bearing extends annularly along the circumferential direction of the first raceway ring 10 for a thrust roller bearing. The first full convex portion 12 of the first raceway ring 10 for a thrust roller bearing may be provided at the center portion of the raceway surface 11 of the first raceway ring 10 for a thrust roller bearing 1 in the radial direction of the thrust roller bearing 1 . The first fully convex portion 12 of the raceway ring 10 for a first thrust roller bearing may protrude from the first outer flat portion 13 and the first inner flat portion 14 toward the first rolling surface 31 of the first roller 30 . The first fully convex portion 12 of the first raceway ring 10 for a thrust roller bearing may be formed so as to be smoothly connected to the first outer flat portion 13 and the second inner flat portion 24 .

The first fully convex portion 22 of the second raceway ring 20 for a thrust roller bearing extends annularly along the circumferential direction of the second raceway ring 20 for a thrust roller bearing. The first full convex portion 22 of the second raceway ring 20 for a thrust roller bearing may be provided at the center portion of the raceway surface 21 of the second raceway ring 20 for a thrust roller bearing 1 in the radial direction of the thrust roller bearing 1 . The first fully convex portion 22 of the second thrust roller bearing raceway ring 20 may protrude from the second outer flat portion 23 and the second inner flat portion 24 toward the first rolling surface 31 of the first roller 30 . The first fully convex portion 22 of the second raceway ring 20 for a thrust roller bearing may be formed so as to be smoothly connected to the first outer flat portion 13 and the second inner flat portion 24 .

Referring to Fig. 5 and Fig. 6, among the radial sections of the thrust roller bearing 1 (the radial section of the first raceway ring 10 for thrust roller bearings, the radial section of the second raceway ring 20 for thrust roller bearings), The shape of the first surface 12s, 22s of the first full convex portion 12, 22 is a first single arc. The first fully convex portion 12 of the first raceway ring 10 for a thrust roller bearing has a partial shape of a circle having a single radius of curvature r ₁ centered on the point O ₁ . The first fully convex portion 22 of the second raceway ring 20 for a thrust roller bearing has a partial shape of a circle having a single radius of curvature r ₂ centered on the point O ₂ .

In this embodiment, the radius of curvature r ₂ of the first full convex portion 22 of the second raceway ring 20 for a thrust roller bearing and the radius of curvature r of the first full convex portion 12 of the first raceway ring 10 for a thrust roller bearing ₁ is equal. The radius of curvature r ₂ of the first full convex portion 22 of the second raceway ring 20 for a thrust roller bearing may be different from the radius of curvature r ₁ of the first full convex portion 12 of the first raceway ring 10 for a thrust roller bearing.

6, the center 31c of the first rolling surface 31 of the first roller 30 in the direction in which the first roller shaft 30r of the first roller 30 extends (the radial direction of the thrust roller bearing 1) can also be aligned with the first The radial center 12c of the thrust roller bearing 1 is in contact with the first full convex portion 12 of the raceway ring 10 for a thrust roller bearing. The center 31c of the first rolling surface 31 of the first roller 30 in the direction in which the first roller shaft 30r of the first roller 30 extends (the radial direction of the thrust roller bearing 1) can also be aligned with the second thrust roller bearing. The radial center 22c of the first full convex portion 22 of the raceway ring 20 is in contact with the thrust roller bearing 1 .

An example of a method of manufacturing the first raceway ring 10 for a thrust roller bearing including the first full convex portion 12 and the second raceway ring 20 for a thrust roller bearing including the first full convex portion 22 may include the following steps. A ring-shaped plate member having a substantially constant thickness is prepared. The first full convex portions 12 , 22 are formed by cutting a portion of the annular plate member so that the first full convex portions 12 , 22 remain.

Another example of the manufacturing method of the first raceway ring 10 for a thrust roller bearing including the first full convex portion 12 and the second raceway ring 20 for a thrust roller bearing including the first full convex portion 22 may include the following steps. A ring-shaped plate member having a substantially constant thickness is prepared. The first full convex portions 12 and 22 are formed by thickening a part of the wall portion of the annular plate member.

The first roller 30 is arranged on the raceway ring 10 for the first thrust roller bearing and the raceway ring 20 for the second thrust roller bearing along the circumferential direction of the raceway ring 10 for the first thrust roller bearing and the raceway ring 20 for the second thrust roller bearing. between 20 orbital circles. The first roller 30 may also be a cylindrical roller or a needle roller. The first rollers 30 respectively have a first rolling surface 31, and the first rolling surface 31 is in contact with the raceway surfaces 11, 21 of the first raceway ring 10 for a thrust roller bearing and the raceway surface 11, 21 of the second raceway ring 20 for a thrust roller bearing, especially The first full convex portions 12, 22 are in contact. The first roller 30 has no protrusions. Therefore, the cost of the thrust roller bearing 1 can be reduced.

Referring to Fig. 4, while the first roller 30 rotates around the first roller shaft 30r in the radial direction of the thrust roller bearing 1, it rotates on the raceway ring for the thrust roller bearing (the raceway ring for the first thrust roller bearing). 10 and the raceway surface 11, 21 of the second thrust roller bearing raceway ring 20). The first roller 30 has a first roller length L ₁ . The first roller length L ₁ is defined as the distance between the first outer end surface 33 of the first roller 30 and the first inner end surface 34 of the first roller 30 on the first roller rotation axis 30r. The first outer end portion 36 of the first rolling surface 31 of the first roller 30 is an end portion of the first rolling surface 31 on the first outer end surface 33 side. The first inner end portion 37 of the first rolling surface 31 of the first roller 30 is an end portion of the first rolling surface 31 on the first inner end surface 34 side. The first roller 30 can also be provided with an inverted groove between the first outer end surface 33 of the first roller 30 and the first rolling surface 31 and between the first outer end surface 33 of the first roller 30 and the first rolling surface 31. corner 32 .

The holder 40 has a plurality of grooves 45 arranged at intervals in the circumferential direction. The first rollers 30 are respectively accommodated in the grooves 45 . The cage 40 holds the first rollers 30 so that the first rollers 30 do not come into contact with each other.

The operating state of the thrust roller bearing 1 of this embodiment will be described. In the operating state of the thrust roller bearing 1, the first roller 30 housed in the groove 45 of the cage 40 is placed on the raceway ring for the thrust roller bearing (the raceway ring 10 for the first thrust roller bearing and the second raceway ring for the thrust roller bearing). The sub-bearing rolls on the track surfaces 11, 21 of the track ring 20). Specifically, the first roller 30 is on the first full convex portion 12 provided on the raceway ring 10 for the first thrust roller bearing and on the first full convex portion 22 provided on the raceway ring 20 for the second thrust roller bearing. Scroll up. The first raceway ring 10 for a thrust roller bearing rotates with respect to the second raceway ring 20 for a thrust roller bearing around the rotation shaft 8 via the first roller 30 .

Examples of this embodiment will be described.

7 shows the rotational speed of the first raceway ring 10 for a thrust roller bearing relative to the second raceway ring 20 for a thrust roller bearing, the rate of temperature rise of the thrust roller bearing 1 of this example, and the thrust roller bearing of Comparative Example 1. The relationship between the temperature rise rate. The rotational speed of the raceway ring 10 for the first thrust roller bearing relative to the raceway ring 20 for the second thrust roller bearing is defined as the speed of the raceway ring 10 for the first thrust roller bearing relative to the raceway ring 20 for the second thrust roller bearing every rotation speed in minutes.

In the thrust roller bearing 1 of this embodiment, the first full convex portion 12 of the raceway ring 10 for the first thrust roller bearing has a curvature radius r ₁ of 520 mm, and the first full convex portion 12 of the raceway ring 20 for the second thrust roller bearing A full convex portion 22 has a radius of curvature r ₂ of 520mm. In the thrust roller bearing of Comparative Example 1, the first full convex portions 12 and 22 are omitted from the thrust roller bearing 1 of the present embodiment.

In the thrust roller bearing 1 of the present embodiment and the thrust roller bearing of Comparative Example 1, the first roller 30 has a first roller length of 5.4 mm along the first roller rotational axis 30 r of the first roller 30 . A thrust load of 3 kN was applied to the thrust roller bearing 1 of this example and the thrust roller bearing of Comparative Example 1. Lubricating oil having a viscosity of ISOVG323 was used for the thrust roller bearing 1 of this example and the thrust roller bearing of Comparative Example 1. The temperature increase rates of the thrust roller bearing 1 of the present embodiment and the thrust roller bearing of Comparative Example 1 are the temperature increase rates of the first main surface 15 and the second main surface 25 .

As shown in FIG. 7 , the temperature rise rate of the thrust roller bearing 1 of the present embodiment and the temperature rise rate of the thrust roller bearing of Comparative Example 1 both increase with the first thrust roller bearing raceway ring 10 relative to the second thrust force. Roller bearings increase with an increase in the rotational speed of the raceway ring 20 . However, the thrust roller bearing 1 of the present embodiment has a lower temperature rise rate of the thrust roller bearing 1 than that of the thrust roller bearing of Comparative Example 1. As shown in Table 1, the heat generation amount of the thrust roller bearing 1 of this example is smaller than that of the thrust roller bearing of Comparative Example 1.

[Table 1]

Example Comparative example 1 Calorific value [W] 2.3 4.8 Central contact surface pressure [GPa] 1.9 1.2 Edge contact surface pressure [GPa] 0.0 2.66

The reason why the thrust roller bearing 1 of this embodiment can reduce the calorific value of the thrust roller bearing 1 and reduce the rate of temperature increase of the thrust roller bearing 1 compared with the thrust roller bearing of Comparative Example 1 will be described below. .

8 shows the relationship between the position d on the first rolling surface 31 of the first roller 30 in the radial direction of the thrust roller bearing ₁ and the heat generation value h1 per unit length at the position d in the present embodiment. In this specification, the calorific value per unit time at position d is defined as the first rolling surface 31 at position d and the raceway surface 11, The heat generated between 21. Fig. 9 shows the position d on the first rolling surface 31 of the first roller 30 in the radial direction of the thrust roller bearing 1 and the first rolling surface 31 and track of the first roller 30 at the position d in this embodiment The relationship between the contact surface pressure P1 between the surfaces ₁₁ and 21. Referring to FIG. 6 , the position of the center 31 c in the radial direction of the thrust roller bearing 1 on the first rolling surface 31 of the first roller 30 is defined as d=0. A position d on the first rolling surface 31 of the first roller 30 located outside the center 31c of the first roller 30 is defined as a positive position (d>0). A position d on the first rolling surface 31 of the first roller 30 located inside the center 31c of the first roller 30 is defined as a negative position (d<0).

At the center 31c of the first roller 30, the first rolling surface 31 of the first roller 30 and the raceway ring for the thrust roller bearing (the raceway ring 10 for the first thrust roller bearing, the raceway for the second thrust roller bearing The track surfaces 11, 21 of the ring 20) are in line contact. At the center 31c of the first roller 30, the peripheral velocity of the raceway surface 11 of the first raceway ring 10 for a thrust roller bearing relative to the raceway surface 21 of the second raceway ring 20 for a thrust roller bearing is the same as that of the first roller 30. The circumferential speeds of the first rolling surface 31 are equal. At the center 31 c of the first roller 30 , the first rolling surface 31 of the first roller 30 does not slide relative to the raceway surfaces 11 , 21 . Therefore, heat generated by differential sliding between the first rolling surface 31 of the first roller 30 and the raceway surfaces 11 , 21 is not generated at the center 31 c of the first roller 30 . The calorific value h ₁ per unit length of the center 31 c of the first roller 30 is 0 [W/mm].

In contrast, as the position d of the first roller 30 moves away from the center 31 c of the first roller 30 , the first rolling surface 31 of the first roller 30 slides more relative to the raceway surfaces 11 , 21 . Specifically, the peripheral velocity of the first rolling surface 31 of the first roller 30 is constant regardless of the position d on the first rolling surface 31 of the first roller 30 . On the other hand, the peripheral velocity of the raceway surface 11 of the first raceway ring 10 for thrust roller bearing relative to the raceway surface 21 of the second raceway raceway 20 for thrust roller bearing follows the speed from the rotation shaft 8 of the thrust roller bearing 1 . It increases toward the outside of the thrust roller bearing 1 . As the position d of the first roller 30 moves away from the center 31c of the first roller 30, the peripheral velocity of the raceway surface 11 of the raceway ring 10 for the first thrust roller bearing and the speed of the first rolling surface 31 of the first roller 30 The difference in peripheral speed becomes larger. Therefore, as the position d of the first roller 30 moves away from the center 31c of the first roller 30, the differential sliding between the first rolling surface 31 of the first roller 30 and the raceway surfaces 11, 21 becomes larger. As the above-mentioned differential sliding becomes larger, the heat generated between the first rolling surface 31 of the first roller 30 and the raceway surfaces 11 , 21 increases. Hereinafter, the aforementioned heat is defined as heat generated due to an increase in the peripheral velocity difference.

As the contact surface pressure P1 between the _first rolling surface 31 of the first roller 30 and the raceway surfaces 11, 21 increases (decreases), due to the above-mentioned differential sliding, the first rolling surface 31 of the first roller 30 The heat generated between the raceway surfaces 11 and 21 increases (decreases). Hereinafter, the aforementioned increased (decreased) heat is defined as heat generated by contact surface pressure.

In this embodiment, the raceway surfaces 11 and 21 of the raceway rings for thrust roller bearings (the raceway rings 10 for the first thrust roller bearing and the raceway rings 20 for the second thrust roller bearings) have contact with the first roller 30. The first full convex portion 12,22. The radial section of the thrust roller bearing 1 (the radial section of the raceway ring for the thrust roller bearing (the raceway ring 10 for the thrust roller bearing and the raceway ring 20 for the second thrust roller bearing)) The shape of the first surface 12s, 22s of the protrusion 12, 22 is a first single arc. The shape of the first surface 12s, 22s of the first full convex portion 12, 22 is a first single circular arc, therefore, the first surface 12s, 22s of the first full convex portion 12, 22 follows the shape of the first roller 30. The position d is away from the center 31c of the first roller 30 and away from the shape of the first rolling surface 31 of the first roller 30 . Therefore, as shown in FIG. 9 , the contact surface pressure P1 between the _first rolling surface 31 of the first roller 30 and the raceway surfaces 11 and 21 increases as the position d of the first roller 30 moves away from the position d of the first roller 30. _The center 31c is reduced, thereby reducing the heat generated by the contact surface pressure P1.

The thrust load is applied to the thrust roller bearing 1 , so that the raceway ring 10 for the first thrust roller bearing, the raceway ring 20 for the second thrust roller bearing and the first roller 30 are elastically deformed. Therefore, in the region A shown in FIG. 8 and FIG. 9 , the first rolling surface 31 of the first roller 30 is in contact with the raceway ring for thrust roller bearing (the raceway ring 10 for the first thrust roller bearing, the second raceway raceway for the thrust roller bearing). The sub-bearings are in line contact with the raceway surfaces 11, 21 of the raceway ring 20). In the region A, the influence of the increase of the peripheral velocity difference on the increase of heat is greater than that of the decrease of the contact surface pressure on the decrease of heat. Therefore, in the region A, the heat generation amount h ₁ per unit length at the position d of the first roller 30 increases as the position d of the first roller 30 moves away from the center 31 c of the first roller 30 .

In the region B shown in FIGS. 8 and 9 , as in the region A, the first rolling surface 31 of the first roller 30 is also in line contact with the raceway surfaces 11 and 21 . However, the shape of the first surface 12s, 22s of the first full convex portion 12, 22 is the first single circular arc, therefore, compared with the area A, in the area B, the first rolling surface 31 of the first roller 30 is in contact with The contact surface pressure P1 between the raceway surfaces ₁₁ , 21 is further reduced. In the region B, the influence of the decrease of the contact surface pressure on the decrease of the heat is greater than the influence of the increase of the peripheral velocity difference on the increase of the heat. Therefore, in the region B, the heat generation amount h ₁ per unit length at the position d of the first roller 30 decreases as the position d of the first roller 30 moves away from the center 31 c of the first roller 30 .

The shape of the first surface 12s, 22s of the first full convex portion 12, 22 is a first single arc. The first surface 12s, 22s of the first full convex portion 12, 22 has a shape that is farther away from the first rolling surface 31 of the first roller 30 as the position d of the first roller 30 is farther away from the center 31c of the first roller 30 . Therefore, in the region C shown in FIG. 8 and FIG. 9, even if the first raceway ring 10 for thrust roller bearing, the second raceway ring 20 for thrust roller bearing, and the first roller 30 are elastically deformed, the first roller bearing The first rolling surface 31 of the child 30 will not be in line contact with the raceway surfaces 11, 21 either.

In the region C, the first rolling surface 31 of the first roller 30 and the raceway ring for a thrust roller bearing (the raceway ring 10 for a thrust roller bearing and the raceway ring 20 for a second thrust roller bearing) do not occur. The differential sliding between the track surfaces 11, 21. In the region C, the first rolling surface 31 of the first roller 30 and the raceway surface of the thrust roller bearing raceway (the first thrust roller bearing raceway ring 10, the second thrust roller bearing raceway ring 30) raceway surface The contact surface pressure P1 between ₁₁ and 21 is zero. In the region C, the heat generation amount h ₁ per unit length at the position d of the first roller 30 is zero. The first full convex portions 12 and 22 of this embodiment can prevent the edge load in Comparative Example 1 described later.

10 shows the relationship between the position d on the first rolling surface 31 of the first roller 30 in the radial direction of the thrust roller bearing 1 of Comparative Example ₁ and the heat generation value h2 per unit length at the position d. 11 shows the position d on the first rolling surface 31 of the first roller 30 in the radial direction of the thrust roller bearing 1 of Comparative Example 1 and the rolling surface of the first roller 30 at the position d and the thrust roller bearing. Use the contact surface between the track surfaces of the track ring to press the relationship between P and ₂ .

In Comparative Example 1, the raceway ring for a thrust roller bearing has a flat raceway surface and does not have the first full convex portions 12 , 22 . The thrust load is applied to the raceway ring for the thrust roller bearing, so that the raceway ring for the thrust roller bearing and the first roller 30 are elastically deformed. Therefore, the first rolling surface 31 of the first roller 30 is in line contact with the raceway surface of the raceway ring for a thrust roller bearing.

As shown in Fig. ₁₁ , the contact surface pressure P2 between the first rolling surface 31 of the first roller 30 and the raceway surface of the raceway ring for thrust roller bearings increases as the position d of the first roller 30 moves away from the first roller. The center 31c of the child 30 is increased. In particular, in Comparative Example 1, at the ends (the first outer end 36 and the first inner end 37 ) of the first rolling surface 31 of the first roller 30 , the first rolling surface 31 of the first roller 30 _The contact surface pressure P2 with the raceway surface of the raceway ring for thrust roller bearings increases sharply. In Comparative Example 1, there was a gap between the ends of the first rolling surface 31 (the first outer end 36 and the first inner end 37 ) of the first roller 30 and the raceway surface of the raceway ring for a thrust roller bearing. Larger edge loads.

Therefore, in Comparative Example ₁ , as the position d of the first roller 30 moves away from the center 31c of the first roller 30, the heat generated by the peripheral velocity difference increases, and the heat generated by the contact surface pressure P2 also increases. As shown in FIG. 10, in Comparative Example 1, as the position d of the first roller 30 is far from the center 31c of the first roller 30, the first rolling surface 31 of the first roller 30 and the thrust roller bearing The heat generated between the orbital surfaces of the orbital ring increases sharply.

In this way, compared with the thrust roller bearing 1 of Comparative Example 1, the thrust roller bearing 1 of this embodiment can make the first rolling surface 31 of the first roller 30 and the raceway ring for thrust roller bearing (the first thrust roller The heat generated between the raceway surfaces 11 and 21 of the raceway ring 10 for the sub-bearing and the raceway ring 20 for the second thrust roller bearing is reduced. Compared with the thrust roller bearing 1 of Comparative Example 1, the thrust roller bearing 1 of this embodiment can suppress the temperature rise of the thrust roller bearing 1 .

As shown in Table 2, the thrust roller bearing 1 of the present embodiment can reduce the friction due to the first rolling surface 31 of the first roller 30 compared with the thrust roller bearing of the comparative example 2 and the comparative example 3. Heat generated by the sliding of the raceway surfaces 11 and 21 of the raceway rings (the raceway ring 10 for the first thrust roller bearing and the raceway ring 20 for the second thrust roller bearing).

[Table 2]

Example Comparative example 2 Comparative example 3 Calorific value [W] 2.3 4.6 3.9 Central contact surface pressure [GPa] 1.9 1.2 1.2

In the thrust bearing of Comparative Example 2, the raceway surface of the raceway ring for a thrust roller bearing has logarithmic full convex portions instead of the first full convex portions 12 , 22 of the thrust roller bearing 1 of this embodiment. The shape of the surface of the logarithmic full convex portion of the radial section of the thrust roller bearing (the radial section of the raceway ring for the thrust roller bearing) is a logarithmic curve. In the thrust bearing of Comparative Example 3, the raceway surface of the raceway ring for a thrust roller bearing has partial protrusions instead of the first full protrusions 12 , 22 of the thrust roller bearing 1 of this embodiment. The partial convex portion refers to a convex portion facing only a part of the rolling surface (first rolling surface 31 ) of the roller (first roller 30 ).

The thrust load is applied to the thrust roller bearing 1 , so that the raceway ring 10 for the first thrust roller bearing, the raceway ring 20 for the second thrust roller bearing and the first roller 30 are elastically deformed. The first rolling surface 31 of the first roller 30 is in line contact with the raceway surfaces 11 and 21 . The shape of the first surface 12s, 22s of the first full convex portion 12, 22 is the first single circular arc, therefore, compared with the comparative example 2 and the comparative example 3, the first roller 30 of the present embodiment can be reduced. The length of the rolling surface 31 in line contact with the raceway surfaces 11 and 21. Therefore, the thrust roller bearing 1 of the present embodiment can reduce the friction caused by the first rolling surface 31 of the first roller 30 relative to the raceway ring for thrust roller bearing (the raceway ring 10 for the first thrust roller bearing, the second thrust roller raceway). Heat generated by the sliding of the raceway surfaces 11 and 21 of the sub-bearing raceway ring 20).

FIG. 12 shows the relationship between the curvature radii r ₁ , r ₂ of the first full convex portions 12 , 22 and the center contact surface pressure and edge contact surface pressure in this embodiment. The edge contact surface pressure is defined as the pressure between the first rolling surface 31 of the first roller 30 and the first rolling surface 31 of the first roller 30 at the ends (first outer end 36, first inner end 37) The contact surface pressure between the raceway surfaces 11 and 21 of the raceway rings for a thrust roller bearing (the first raceway ring 10 for a thrust roller bearing and the second raceway ring 20 for a thrust roller bearing) of this embodiment. The central contact surface pressure is defined as the contact between the first rolling surface 31 of the first roller 30 and the raceway ring for a thrust roller bearing (the raceway ring for a first thrust roller bearing) of this embodiment at the center 31c of the first roller 30. 10. The contact surface pressure between the raceway surfaces 11 and 21 of the raceway ring 20) for the second thrust roller bearing.

When the edge contact surface pressure increases, at the contact portion between the ends (first outer end 36, first inner end 37) of the first rolling surface 31 of the first roller 30 and the raceway surfaces 11, 21, The raceway rings for the thrust roller bearing (the raceway ring 10 for the first thrust roller bearing and the raceway ring 20 for the second thrust roller bearing) were damaged. In order to prevent damage to such raceway rings for thrust roller bearings (first raceway ring 10 for thrust roller bearings, second raceway ring 20 for thrust roller bearings), the edge contact surface pressure may be 2.6 Gpa or less, or It may be 2.49 GPa or less, may be 2.15 GPa or less, or may be 1.6 GPa or less. In order to prevent such damage to the raceway rings for thrust roller bearings (the first raceway ring 10 for thrust roller bearings and the second raceway ring 20 for thrust roller bearings), the first full convex parts 12 and 22 of the present embodiment are The radii of curvature r ₁ and r ₂ may be 2100 mm or less, 2000 nm or less, 1600 mm or less, or 1200 mm or less.

The raceway surfaces 11, 21 of the raceway rings for thrust roller bearings (the first raceway ring 10 for thrust roller bearings, the second raceway ring 20 for thrust roller bearings) of this embodiment have first full convex portions 12, 22 . Therefore, as shown in FIGS. 9 and 11 , the central contact surface pressure (P ₁ (d=0)) of the present embodiment is higher than that of Comparative Example 1 (P ₂ (d=0)).

When the central contact surface pressure of this embodiment becomes large, the center 31c of the first roller 30 and the raceway ring for thrust roller bearing of this embodiment (the raceway ring 10 for the first thrust roller bearing, the second thrust roller bearing) At the contact portion of the raceway surfaces 11 and 21 of the raceway ring 20 for the sub-bearing, the raceway ring for the thrust roller bearing of this embodiment (the raceway ring 10 for the first thrust roller bearing, the raceway ring for the second thrust roller bearing 20) Breakage will occur. In order to prevent such damage to the raceway rings for thrust roller bearings (the raceway rings 10 for the first thrust roller bearings and the second raceway rings 20 for thrust roller bearings), the central contact surface pressure in this embodiment may be 2.0Gpa It may be less than or equal to 1.8 GPa, or less than 1.7 GPa, or less than 1.67 GPa. In order to prevent such damage to the raceway rings for thrust roller bearings (the first raceway ring 10 for thrust roller bearings and the second raceway ring 20 for thrust roller bearings), the first full convex parts 12 and 22 of the present embodiment are The curvature radii r ₁ and r ₂ may be not less than 250 mm, not less than 445 mm, not less than 600 mm, or not less than 720 mm.

Effects of the thrust roller bearing 1 and the raceway rings for a thrust roller bearing (the first raceway ring 10 for a thrust roller bearing and the second raceway ring 20 for a thrust roller bearing) of this embodiment will be described.

The thrust roller bearing 1 of this embodiment includes: a raceway ring 10 for a first thrust roller bearing, a raceway ring 20 for a second thrust roller bearing, and a plurality of first rollers 30. The first raceway ring 10 for a thrust roller bearing and the second raceway ring 20 for a thrust roller bearing are disposed between the first raceway ring 10 for a thrust roller bearing and the second raceway 20 for a thrust roller bearing in the circumferential direction. The first raceway ring 10 for a thrust roller bearing and the second raceway ring 20 for a thrust roller bearing respectively include raceway surfaces 11 and 21 on which the first rollers 30 roll. At least one of the raceway surface 11 of the first raceway ring 10 for a thrust roller bearing and the raceway surface 21 of the second raceway ring 20 for a thrust roller bearing has a first full convex portion 12 , 22 in contact with the first roller 30 . The shape of the first surfaces 12s, 22s of the first full convex portions 12, 22 in the radial section of the thrust roller bearing 1 is a first single arc.

The shape of the first surface 12s, 22s is the first full convex portion 12, 22 of the first single arc, which can reduce the heat generated by the peripheral velocity difference and the heat generated by the contact surface pressure. The thrust roller bearing 1 of the present embodiment can reduce the pressure caused by the first rolling surface 31 of the first roller 30 relative to the raceway ring for a thrust roller bearing (the raceway ring 10 for a first thrust roller bearing, the raceway ring 10 for a second thrust roller bearing). Heat generated by the sliding of the raceway surfaces 11 and 21 of the raceway ring 20). The thrust roller bearing 1 of this embodiment can prevent the raceway surface 11 of the thrust roller bearing raceway (the first thrust roller bearing raceway 10 and the second thrust roller bearing raceway 20 ) from being damaged due to the above-mentioned heat. , 21 produces surface starting point peeling.

The shape of the first surface 12s, 22s is the first full convex part 12, 22 of the first single arc, which can reduce the difference between the ends (the first outer end 36, the first inner end 37) and the first roller 30. Edge load generated between raceway surfaces 11 and 21 of raceway rings for thrust roller bearings (first raceway ring 10 for thrust roller bearing, second raceway ring 20 for thrust roller bearing). The thrust roller bearing 1 of the present embodiment can prevent the raceway rings for a thrust roller bearing (the first raceway ring 10 for a thrust roller bearing and the second raceway ring 20 for a thrust roller bearing) from being damaged by the above-mentioned edge load.

In the thrust roller bearing 1 of the present embodiment, the first single arc has curvature radii r ₁ , r ₂ of not less than 250 mm and not more than 2100 mm. Therefore, damage to the raceway rings for thrust roller bearings (first raceway ring 10 for thrust roller bearings, second raceway rings 20 for thrust roller bearings) can be prevented.

The raceway rings for thrust roller bearings (the first raceway ring 10 for thrust roller bearings and the second raceway ring 20 for thrust roller bearings) of this embodiment include raceway surfaces 11 and 21 on which a plurality of first rollers 30 roll. . The raceway surfaces 11 , 21 have first full convex portions 12 , 22 that are in contact with the first rollers 30 . The first surfaces 12s, 12s, The shape of 22s is a first single circular arc.

The shape of the first surface 12s, 22s is the first full convex portion 12, 22 of the first single arc, which can reduce the heat generated by the peripheral velocity difference and the heat generated by the contact surface pressure. The raceway rings for thrust roller bearings (the first raceway ring 10 for thrust roller bearings and the second raceway ring 20 for thrust roller bearings) of this embodiment can reduce the Heat generated by the sliding of the raceway surfaces 11 and 21 of the rings (the raceway ring 10 for the first thrust roller bearing and the raceway ring 20 for the second thrust roller bearing). The raceway rings for thrust roller bearings (the first raceway ring 10 for thrust roller bearings, the second raceway ring 20 for thrust roller bearings) of this embodiment can prevent the The first raceway ring 10 for a thrust roller bearing and the raceway surface 11 and 21 of the second raceway ring 20 for a thrust roller bearing have peeling off at the origin of the surface.

The shape of the first surface 12s, 22s is the first full convex part 12, 22 of the first single arc, which can reduce the difference between the ends (the first outer end 36, the first inner end 37) and the first roller 30. Edge load generated between raceway surfaces 11 and 21 of raceway rings for thrust roller bearings (first raceway ring 10 for thrust roller bearing, second raceway ring 20 for thrust roller bearing). The raceway rings for thrust roller bearings (the first raceway ring 10 for thrust roller bearings and the second raceway ring 20 for thrust roller bearings) of this embodiment can prevent the raceway rings for thrust roller bearings ( The raceway ring 10 for the first thrust roller bearing and the raceway ring 20 for the second thrust roller bearing are damaged.

In the raceway rings for thrust roller bearings (the first raceway ring 10 for thrust roller bearings, the second raceway ring 20 for thrust roller bearings) of this embodiment, the first single arc has a curvature of not less than 250 mm and not more than 2100 mm Radius r ₁ , r ₂ . Therefore, damage to the raceway rings for thrust roller bearings (first raceway ring 10 for thrust roller bearings, second raceway rings 20 for thrust roller bearings) can be prevented.

(Embodiment 2)

A thrust roller bearing 1a and raceway rings for a thrust roller bearing (first raceway ring 10a for a thrust roller bearing, second raceway ring 20a for a thrust roller bearing) according to Embodiment 2 will be described with reference to FIG. 13 . The thrust roller bearing 1a and the raceway rings for thrust roller bearings (the first raceway ring 10a for thrust roller bearings and the second raceway ring 20a for thrust roller bearings) of this embodiment include the thrust roller bearing bearings of Embodiment 1. 1 and the raceway rings for thrust roller bearings (the first raceway ring 10 for thrust roller bearings and the second raceway ring 20 for thrust roller bearings) have the same structure, but mainly differ in the following points.

In the thrust roller bearing 1a of this embodiment, the first roller 30a is a tapered roller. The first roller 30 a that is a tapered roller has a diameter that gradually increases from the first inner end portion 37 toward the first outer end portion 36 .

In the thrust roller bearing 1a of this embodiment, the raceway surfaces 11a and 21a of the first raceway ring 10a for a thrust roller bearing do not include the first outer flat portion 13 and the first inner flat portion shown in FIGS. 2 and 5 . 14. The first raceway ring 10a for a thrust roller bearing includes a first outer flange portion 51 located on the outer side of the raceway surface 11a and a first inner flange portion 52 located on the inner side of the raceway surface 11a. The first outer flange portion 51 and the first inner flange portion 52 restrict the position of the first roller 30 a in the radial direction of the thrust roller bearing 1 a. At least one of the first outer eaves 51 and the first inner eaves 52 may be in contact with the first roller 30a to guide the first roller 30a.

In the thrust roller bearing 1a of this embodiment, the raceway surfaces 11a, 21a of the second raceway ring 20a for a thrust roller bearing do not include the second outer flat portion 23 and the second inner flat portion shown in FIGS. 3 and 5 . twenty four. The second raceway ring 20a for a thrust roller bearing includes a second outer flange portion 56 located on the outer side of the raceway surface 21a and a second inner flange portion 57 located on the inner side of the raceway surface 21a. The second outer flange portion 56 and the second inner flange portion 57 restrict the position of the first roller 30 a in the radial direction of the thrust roller bearing 1 a. At least one of the second outer eaves 56 and the second inner eaves 57 may be in contact with the first roller 30a to guide the first roller 30a.

A thrust roller bearing 1b and raceway rings for a thrust roller bearing (first raceway ring 10a for a thrust roller bearing, second raceway ring 20a for a thrust roller bearing) according to a modified example of this embodiment will be described with reference to FIG. 14 . The thrust roller bearing 1b and the raceway rings for thrust roller bearings (the first raceway ring 10a for thrust roller bearings, the second raceway ring 20 for thrust roller bearings) of the modified example of this embodiment include the same thrust The roller bearing 1a and the raceway ring for a thrust roller bearing (the first raceway ring 10a for a thrust roller bearing, the second raceway ring 20a for a thrust roller bearing) have the same structure, but mainly differ in the following points.

The second raceway ring 20 for a thrust roller bearing according to the modified example of the present embodiment has the same structure as that of the second raceway ring 20 for a thrust roller bearing in the first embodiment. The raceway surface 21 of the second raceway ring 20 for a thrust roller bearing according to the modified example of the present embodiment includes a second outer flat portion 23 and a second inner flat portion 24 . A second raceway ring 20 for a thrust roller bearing according to a modified example of the present embodiment includes a second outer flange portion 56 and a second inner flange portion 57 shown in FIG. 13 .

A cage 40b according to a modified example of the present embodiment includes an inclined portion 43 that is separated from the raceway surface 21 of the second raceway ring 20 for a thrust roller bearing 1b as it goes from the inside to the outside of the thrust roller bearing 1b. tilt. The groove 45 for accommodating the first roller 30 a is arranged on the inclined portion 43 .

The effects of the thrust roller bearings 1 a and 1 b of the present embodiment and its modifications exhibit the following effects in addition to the effects of the thrust roller bearing 1 of the first embodiment.

The first roller 30 a that is a tapered roller has a diameter that gradually increases from the first inner end portion 37 toward the first outer end portion 36 . The peripheral velocity of the first rolling surface 31 of the first roller 30 a increases from the first inner end portion 37 toward the first outer end portion 36 . The first roller 30a as a tapered roller can reduce the first rolling surface of the first roller 30a in the radial direction of the thrust roller bearing 1a, 1b (the direction in which the first roller shaft of the first roller 30a extends). 31 and the difference between the peripheral velocity of the raceway surface 11a of the first raceway ring 10a for a thrust roller bearing.

Therefore, the thrust roller bearings 1a and 1b of the present embodiment and its modifications can reduce the number of first rollers 30a relative to the thrust roller bearing raceway (the first thrust roller bearing raceway 10a, the second thrust roller bearing raceway). The sliding of the raceway surfaces 11a, 21, 21a of the bearing raceway rings 20, 20a) reduces the heat generated by the above-mentioned sliding. The thrust roller bearings 1a and 1b of this embodiment can prevent the raceway rings for thrust roller bearings (the first raceway rings for thrust roller bearings 10 and the second raceway rings for thrust roller bearings 20 and 20a) from being damaged due to the above-mentioned heat. The surface starting point peeling occurs on the track surfaces 11a, 21, 21a.

(Embodiment 3)

The thrust roller bearing 1c and the raceway rings for thrust roller bearings (first raceway ring 10c for thrust roller bearing, second raceway ring 20c for thrust roller bearing) of Embodiment 3 will be described with reference to FIGS. 15 to 17 . The thrust roller bearing 1c and the raceway rings for the thrust roller bearing (the first raceway ring 10c for the thrust roller bearing and the second raceway ring 20c for the thrust roller bearing) of this embodiment include the thrust roller bearing of the first embodiment. 1 and the raceway rings for thrust roller bearings (the first raceway ring 10 for thrust roller bearings and the second raceway ring 20 for thrust roller bearings) have the same structure, but mainly differ in the following points.

As shown in FIG. 15 , the thrust roller bearing 1 c of this embodiment includes a plurality of rows of rollers (first roller 30 c, second roller 60 ). Specifically, the thrust roller bearing 1c of this embodiment further includes a plurality of second rollers 60 between the first raceway ring 10c for a thrust roller bearing and the second raceway ring 20c for a thrust roller bearing. The second roller 60 is arranged along the circumferential direction of the first raceway ring 10c for a thrust roller bearing and the second raceway ring 20c for a thrust roller bearing. The second roller 60 is arranged inside the first roller 30c. The second roller 60 rolls on the raceway surfaces 11c, 21c of the raceway rings for thrust roller bearings (the first raceway ring 10c for thrust roller bearings, the second raceway ring 20c for thrust roller bearings).

In this embodiment, the raceway surface 11c of the first raceway ring 10c for a thrust roller bearing has the second fully convex portion 16 in contact with the second roller 60, and the raceway surface 11c of the second raceway ring 20c for a thrust roller bearing 21c has the second full convex portion 26 in contact with the second roller 60 . At least one of the raceway surface 11c of the first raceway ring 10c for a thrust roller bearing and the raceway surface 21c of the second raceway ring 20c for a thrust roller bearing may have a second full convex portion in contact with the second roller 60 16, 26. The second full convex portion 16 is located inside the first full convex portion 12 , and the second full convex portion 26 is located inside the first full convex portion 22 .

The first raceway ring 10 c for a thrust roller bearing may have the first inner flat portion 14 on the outer side of the second full convex portion 16 . The first raceway ring 10 c for a thrust roller bearing may have a third flat portion 17 inside the second fully convex portion 16 . The second full convex portion 16 may protrude from the first inner flat portion 14 and the third flat portion 17 toward the first rolling surface 31 of the first roller 30 . The second full convex portion 16 may also be formed to be smoothly connected to the first inner flat portion 14 and the third flat portion 17 .

The second raceway ring 20c for a thrust roller bearing may have the second inner flat portion 24 on the outer side of the second fully convex portion 26 . The second raceway ring 20 c for a thrust roller bearing may have a fourth flat portion 27 inside the second fully convex portion 26 . The second full convex portion 26 may protrude from the second inner flat portion 24 and the fourth flat portion 27 toward the first rolling surface 31 of the first roller 30 . The second full convex portion 26 may also be formed to be smoothly connected to the second inner flat portion 24 and the fourth flat portion 27 .

The raceway surface 11 c includes a first surface 12 s of the first full convex portion 12 and a second surface 16 s of the second full convex portion 16 . The raceway surface 11 c may further include a first outer flat portion 13 on the outer side of the first full convex portion 12 . The raceway surface 21 c includes a first surface 22 s of the first full convex portion 22 and a second surface 26 s of the second full convex portion 26 . The raceway surface 21 c may further include a second outer flat portion 23 on the outer side of the first fully convex portion 22 .

In the radial section of the thrust roller bearing 1c (the radial section of the first raceway ring 10c for a thrust roller bearing, the radial section of the second raceway ring 20c for a thrust roller bearing), the second full convex portion 16, The shape of the second surface 16s, 26s of 26 is a second single arc. The radius of curvature of the second full convex portion 16 , 26 may be equal to the radius of curvature of the first full convex portion 12 , 22 . The radius of curvature of the second full convex portion 16 , 26 may be different from the radius of curvature of the first full convex portion 12 , 22 .

In order to prevent the raceway rings for thrust roller bearings (the first raceway ring 10c for thrust roller bearing, the second raceway ring 20c for thrust roller bearing) from The contact portion between the second inner end portion 67) and the raceway rings for thrust roller bearings (first raceway ring 10c for thrust roller bearings, second raceway ring 20c for thrust roller bearings) is damaged at the contact portion of the raceway surfaces 11c, 21c. The radius of curvature of the second full convex portions 16 and 26 in the embodiment may be 2100 mm or less, 2000 nm or less, 1600 mm or less, or 1200 mm or less. In order to prevent the above-mentioned damage to the raceway rings for thrust roller bearings (the first raceway ring 10c for thrust roller bearings and the second raceway ring 20c for thrust roller bearings) of this embodiment, the second fully convex The radius of curvature of the portions 16 and 26 may be 250 mm or more, 445 mm or more, 600 mm or more, or 720 mm or more.

The first roller 30c of this embodiment has the same structure as the first roller 30 of Embodiment 1, but differs in the following points. The first roller length L _1c (see FIG. 16 ) of the first roller 30c in the present embodiment is shorter than the first roller length L ₁ (see FIG. 4 ) of the first roller 30 in the first embodiment.

Referring to Fig. 17, the second roller 60 has a _second roller length L2. The second roller length L ₂ is defined as the distance between the second outer end surface 63 of the second roller 60 and the second inner end surface 64 of the second roller 60 on the second roller rotation axis 60r. The second roller 60 rotates around the second roller rotating shaft 60r along the radial direction of the thrust roller bearing 1c, and rotates on the raceway ring for the thrust roller bearing (the raceway ring for the first thrust roller bearing 10c, the second raceway ring for the thrust roller bearing The thrust roller bearing rolls on the raceway surfaces 11c, 21c of the raceway ring 20c). The second outer end portion 66 of the second rolling surface 61 of the second roller 60 is an end portion of the second rolling surface 61 on the second outer end surface 63 side. The second inner end portion 67 of the second rolling surface 61 of the second roller 60 is an end portion of the second rolling surface 61 on the second inner end surface 64 side. The second roller 60 can also be provided with an inverted groove between the second outer end surface 63 of the second roller 60 and the second rolling surface 61 and between the second inner end surface 64 of the second roller 60 and the second rolling surface 61. corner 62 .

The second roller 60 of the present embodiment has the same structure as the first roller 30 of the first embodiment, but differs in the following points. The second roller length L ₂ (see FIG. 17 ) of the second roller 60 in the present embodiment is shorter than the first roller length L ₁ (see FIG. 4 ) of the first roller 30 in the first embodiment. The sum of the first roller length L1c of the first roller _30c and the second roller length L2 of the _second roller 60 in this embodiment may be shorter than the _first roller length L1 of the first embodiment. The second roller 60 may also have the same structure as the first roller 30c.

The thrust roller bearing 1c and the thrust roller bearing raceway (the first thrust roller bearing raceway 10c, the second thrust roller bearing raceway 20c) of the present embodiment have effects other than the thrust roller bearings of the first embodiment. In addition to the effects of the bearing 1 and the raceway rings for thrust roller bearings (the first raceway ring 10 for thrust roller bearings and the second raceway ring 20 for thrust roller bearings), the following effects are also achieved.

The thrust roller bearing 1c of this embodiment further includes a plurality of second rollers 60, and the plurality of second rollers 60 are arranged along the first raceway ring 10c for a thrust roller bearing and the raceway ring 20c for a second thrust roller bearing. It is disposed in the circumferential direction between the first raceway ring 10c for a thrust roller bearing and the second raceway ring 20c for a thrust roller bearing. The second roller 60 rolls on the raceway surface 11c of the first raceway ring 10c for a thrust roller bearing and the raceway surface 21c of the second raceway ring 20c for a thrust roller bearing. At least one of the raceway surface 11c of the first raceway ring 10c for a thrust roller bearing and the raceway surface 21c of the second raceway ring 20c for a thrust roller bearing has a second full convex portion 16, 26 that contacts the second roller 60 . The second full convex portion 16 , 26 is located inside the first full convex portion 12 , 22 . The shape of the second surface 16s, 26s of the second full convex portion 16, 26 in the radial section of the thrust roller bearing 1c is a second single arc.

The thrust roller bearing 1c of this embodiment includes a first roller 30c and a second roller 60 between the first raceway ring 10c for a thrust roller bearing and the second raceway ring 20c for a thrust roller bearing. The second roller 60 in contact with the second full convex portion 16 , 26 is arranged inside the first roller 30 c in contact with the first full convex portion 12 , 22 . The peripheral velocity of the second rolling surface 61 of the second roller 60 can be made lower than the peripheral velocity of the second rolling surface 61 of the first roller 30c.

The second difference between the peripheral velocity of the raceway surface 11c of the raceway ring 10c for the first thrust roller bearing of this embodiment and the peripheral velocity of the first rolling surface 31 of the first roller 30c and the first thrust force of the first embodiment The first difference between the peripheral speed of the raceway surface 11 of the raceway ring 10 for a roller bearing and the peripheral speed of the first rolling surface 31 of the first roller 30 is reduced. The third difference between the peripheral velocity of the raceway surface 11c of the raceway ring 10c for the first thrust roller bearing of this embodiment and the peripheral velocity of the second rolling surface 61 of the second roller 60 is equal to the first thrust force of the first embodiment. The first difference between the peripheral speed of the raceway surface 11 of the raceway ring 10 for a roller bearing and the peripheral speed of the first rolling surface 31 of the first roller 30 is reduced.

Therefore, compared with the first rolling surface 31 of the first roller 30 in Embodiment 1, the first rolling surface 31 of the first roller 30c and the second rolling surface 61 of the second roller 60 in this embodiment are relatively The rolling surfaces 11c, 21c slide less. The thrust roller bearing 1c of this embodiment can reduce the heat generated by the sliding of the first rolling surface 31 of the first roller 30c and the second rolling surface 61 of the second roller 60 with respect to the raceway surfaces 11c and 21c. The thrust roller bearing 1c of the present embodiment can prevent the raceway surface 11c of the thrust roller bearing raceway (the first thrust roller bearing raceway 10c, the second thrust roller bearing raceway 20c) from being damaged due to the above-mentioned heat. , 21c produces surface origin peeling.

The shape of the second surface 16s, 26s is that the second full convex portion 16, 26 of the second single arc can be reduced at the ends of the second roller 60 (the first outer end 66, the second inner end 67). The second rolling surface 61 of the second roller 60 and the raceway surfaces 11c and 21c of the raceway rings for the thrust roller bearing (the raceway ring 10c for the first thrust roller bearing and the raceway ring 20c for the second thrust roller bearing) contact surface pressure. The shape of the second surface 16s, 26s is the second full convex portion 16, 26 of the second single arc, which can reduce the difference between the ends (the second outer end 66, the second inner end 67) and the second roller 60. The edge load generated between the raceway surfaces 11c and 21c of the raceway rings for thrust roller bearings (the first raceway ring for thrust roller bearings 10c and the second raceway ring for thrust roller bearings 20c). The thrust roller bearing 1c of the present embodiment can prevent the raceway rings for a thrust roller bearing (the first raceway ring 10c for a thrust roller bearing and the second raceway ring 20c for a thrust roller bearing) from being damaged by the aforementioned edge load.

In the thrust roller bearing 1c of this embodiment, not only the first roller 30c receives a load but also the second roller 60 receives a thrust load. Therefore, the thrust roller bearing 1c of this embodiment can withstand a larger thrust load.

In the thrust roller bearing 1c of the present embodiment, the second single arc may have a curvature radius of not less than 250 mm and not more than 2100 mm. Therefore, damage to the raceway rings for thrust roller bearings (first raceway ring 10c for thrust roller bearings, second raceway rings 20c for thrust roller bearings) can be prevented.

The raceway rings for thrust roller bearings (the first raceway ring 10c for thrust roller bearings, the second raceway ring 20c for thrust roller bearings) of the present embodiment further have a second fully convex raceway in contact with the plurality of second rollers 60 . 16, 26, the plurality of second rollers 60 roll on the track surfaces 11c, 21c. The second full convex portion 16 , 26 is located inside the first full convex portion 12 , 22 . The second surfaces 16s, 16s, and The shape of 26s is the second single arc.

The raceway rings for thrust roller bearings of this embodiment (first raceway ring 10c for thrust roller bearings, second raceway ring 20c for thrust roller bearings) include first full convex portions 12, 22 and second full convex portions 16 , 26, the second full convex portion 16,26 is located inside the first full convex portion 12,22. The 2nd roller 60 which contacts the 2nd full convex part 16,26 can be arrange|positioned inside the 1st roller 30c. Therefore, the peripheral velocity of the second rolling surface 61 of the second roller 60 can be made lower than the peripheral velocity of the first rolling surface 31 of the first roller 30a.

The second difference between the peripheral velocity of the raceway surface 11c of the raceway ring 10c for the first thrust roller bearing of this embodiment and the peripheral velocity of the first rolling surface 31 of the first roller 30c and the first thrust force of the first embodiment The first difference between the peripheral speed of the raceway surface 11 of the raceway ring 10 for a roller bearing and the peripheral speed of the first rolling surface 31 of the first roller 30 is reduced. The third difference between the peripheral velocity of the raceway surface 11c of the raceway ring 10c for the first thrust roller bearing of this embodiment and the peripheral velocity of the second rolling surface 61 of the second roller 60 is equal to the first thrust force of the first embodiment. The first difference between the peripheral speed of the raceway surface 11 of the raceway ring 10 for a roller bearing and the peripheral speed of the first rolling surface 31 of the first roller 30 is reduced.

Therefore, compared with the first rolling surface 31 of the first roller 30 in Embodiment 1, the first rolling surface 31 of the first roller 30c and the second rolling surface 61 of the second roller 60 in this embodiment are relatively The rolling surfaces 11c, 21c slide less. The raceway rings for thrust roller bearings (the first raceway ring 10c for thrust roller bearings and the second raceway ring 20c for thrust roller bearings) of this embodiment can reduce the The second rolling surface 61 of the second roller 60 slides on the raceway surfaces 11c, 21c of the raceway rings for the thrust roller bearing (the raceway ring 10c for the first thrust roller bearing, and the raceway ring 20c for the second thrust roller bearing). generated heat. The raceway rings for thrust roller bearings (the first raceway ring for thrust roller bearings 10c, the second raceway ring for thrust roller bearings 20c) of this embodiment can prevent the On the raceway surfaces 11c and 21c of the raceway ring 10c for a thrust roller bearing and the raceway ring 20c for a second thrust roller bearing, peeling occurs at the origin of the surface.

The shape of the second surface 16s, 26s is that the second full convex portion 16, 26 of the second single arc can be reduced at the end of the second roller 60 (the second outer end 66, the second inner end 67). The contact surface pressure between the second rolling surface 61 of the second roller 60 and the raceway surfaces 11c, 21c. The shape of the second surface 16s, 26s is the second full convex portion 16, 26 of the second single arc, which can reduce the difference between the ends (the second outer end 66, the second inner end 67) and the second roller 60. The edge load generated between the track surfaces 11c, 21c. The raceway rings for thrust roller bearings (the first raceway ring 10c for thrust roller bearings, the second raceway ring 20c for thrust roller bearings) of this embodiment can prevent the raceway rings for thrust roller bearings ( The raceway ring 10c for the first thrust roller bearing and the raceway ring 20c) for the second thrust roller bearing were damaged.

In the raceway rings for thrust roller bearings (the first raceway ring 10c for thrust roller bearings, the second raceway ring 20c for thrust roller bearings) of the present embodiment, the second single arc may have a diameter of not less than 250 mm and not more than 2100 mm. radius of curvature. Therefore, damage to the raceway rings for thrust roller bearings (first raceway ring 10c for thrust roller bearings, second raceway rings 20c for thrust roller bearings) can be prevented.

It should be understood that the embodiment disclosed this time is an illustration in all points and is not restrictive. For example, at least one of the first outer eaves 51, the first inner eaves 52, the second outer eaves 56, and the second inner eaves 57 of Embodiment 2 and its modified examples may be provided in Embodiments 1 and 2. Thrust roller bearing 1c of Embodiment 3. The scope of the present invention is shown by the claims rather than the above description, and the present invention includes all changes within the meaning and range equivalent to the claims.

Symbol Description

1, 1a, 1b, 1c thrust roller bearings; 8 rotating shafts; 10, 10a, 10c first raceway rings for thrust roller bearings; 11, 11a, 11c raceway surfaces; 12, 22 first full convex part; 12c, 22c Center; 12s, 22s first surface; 13 first outer flat part; 14 first inner flat part; 15 first main surface; 16, 26 second full convex part; 16s, 26s second surface; 17 third flat part ; 20, 20a, 20c second raceway ring for thrust roller bearing; 21, 21a, 21c raceway surface; 23 second outer flat portion; 24 second inner flat portion; 25 second main surface; 27 fourth flat portion; 30, 30a, 30c first roller; 30r first roller shaft; 31 first rolling surface; 31c center; 32, 62 chamfer; 33 first outer end face; 34 first inner end face; 36 first outer end 37 first inner end; 40, 40b retainer; 43 inclined portion; 45 groove; 51 first outer eaves; 52 first inner eaves; 56 second outer eaves; 57 second inner eaves 60 second roller; 60r second roller shaft; 61 second rolling surface; 63 second outer end surface; 64 second inner end surface; 66 second outer end; 67 second inner end.

Claims (11)

1. a kind of thrust roller bearing, comprising:

First thrust roller bearing rail ring；

Second thrust roller bearing rail ring；And

Multiple first rollers, multiple first rollers are pushed away along the first thrust roller bearing rail ring and described second Power roller bearing rail ring it is arranged circumferentially in the first thrust roller bearing rail ring and second thrust roller Between bearing rail ring,

The first thrust roller bearing rail ring and second thrust roller bearing are respectively included with rail ring for institute The orbital plane of the first roller rolls is stated,

The orbital plane of the first thrust roller bearing rail ring and the second thrust roller bearing rail ring At least one of the orbital plane there is the first full protrusion with first roller contact, the thrust roller bearing The shape of the first surface of the described first full protrusion in radial section is first single circular arc.

2. thrust roller bearing as described in claim 1, wherein

Described first single circular arc has 250mm or more and 2100mm radius of curvature below.

3. thrust roller bearing as claimed in claim 1 or 2, wherein

Center of the rolling surface of first roller in the axial direction of first roller and the described first full protrusion are in the diameter Upward central contact.

4. thrust roller bearing as claimed any one in claims 1 to 3, wherein

First roller is cylinder roller or needle rollers.

5. thrust roller bearing as claimed any one in claims 1 to 3, wherein

First roller is taper roller.

6. the thrust roller bearing as described in any one of claims 1 to 5, wherein

It further include multiple second rollers, multiple second rollers are along the first thrust roller bearing rail ring and described Second thrust roller bearing rail ring it is described arranged circumferentially in the first thrust roller bearing rail ring and described the Between two thrust roller bearing rail rings,

Second roller is rolled in the orbital plane of the first thrust roller bearing rail ring and second thrust It is rolled in the orbital plane of sub- bearing rail ring,

The orbital plane of the first thrust roller bearing rail ring and the second thrust roller bearing rail ring At least one of the orbital plane there is the second full protrusion with second roller contact, the second full protrusion is located at The shape of the inside of the first full protrusion, the second surface of the described second full protrusion in the radial section is Second single circular arc.

7. thrust roller bearing as claimed in claim 6, wherein

Described second single circular arc has 250mm or more and 2100mm radius of curvature below.

8. a kind of thrust roller bearing rail ring,

Including orbital plane, multiple first rollers roll in the orbital plane,

The orbital plane has the first full protrusion with first roller contact, the diameter of the thrust roller bearing rail ring The shape of the first surface of the described first full protrusion into section is first single circular arc.

9. thrust roller bearing rail ring as claimed in claim 8, wherein

Described first single circular arc has 250mm or more and 2100mm radius of curvature below.

10. thrust roller bearing rail ring as claimed in claim 8 or 9, wherein

The orbital plane has the second full protrusion, the second full protrusion and multiple second rollers rolled in the orbital plane Contact,

The second full protrusion is located at the inside of the described first full protrusion, and described second in the radial section is complete convex The shape of the second surface in portion is second single circular arc.

11. thrust roller bearing rail ring as claimed in claim 10, wherein

Described second single circular arc has 250mm or more and 2100mm radius of curvature below.