A thrust bearing

Abstract

The present invention provides a thrust bearing, comprising a shaft ring (1) and a seat ring (2), wherein a first annular groove centered on the axis of the thrust bearing is provided on a side of the shaft ring (1) facing the seat ring (2); a second annular groove centered on the axis of the thrust bearing is provided on a side of the seat ring (2) facing the shaft ring (1); the first annular grooves and the second annular grooves are directly interlaced with each other, or are respectively matched with annular protrusions on the circumference of the rolling body (3) via a rolling body (3). The thrust bearing provided by the present invention achieves a large load-bearing capacity and a high limit speed through a relatively simple structure.

Description

Technical Field

[0001] The present invention relates to the technical field of bearings, and in particular to a thrust bearing. Background Art

[0002] Current thrust bearings generally suffer from insufficient radial load capacity. To achieve a high radial load capacity, thrust bearings typically require complex designs, resulting in a large volume and often a low limiting speed. Therefore, improving thrust bearings to achieve both high load capacity and high limiting speeds with a relatively simple structure has become a pressing technical challenge for those skilled in the art. Summary of the Invention

[0003] In view of this, the present invention provides a thrust bearing, which achieves a larger load-bearing capacity and a higher limit speed through a relatively simple structure.

[0004] In order to achieve the above object, the present invention provides the following technical solutions:

[0005] A thrust bearing comprises a shaft ring and a seat ring, wherein a surface of the shaft ring facing the seat ring is provided with a plurality of first annular grooves centered on the axis of the thrust bearing;

[0006] A surface of the seat ring facing the shaft ring is provided with a plurality of second annular grooves centered on the axis of the thrust bearing;

[0007] The first annular groove and the second annular groove are directly interlaced and matched, or are respectively matched with the annular protrusions on the circumferential surface of the rolling body through the rolling body.

[0008] Optionally, in the thrust bearing, the thrust bearing is a thrust roller bearing, comprising a rolling element, wherein a plurality of corrugated rings arranged along the axial direction of the rolling element are provided on the circumferential surface of the rolling element, and the corrugated rings are annular protrusions centered on the axis of the rolling element;

[0009] The shaft ring and the seat ring are both provided with a plurality of raceway grooves on the pressure-bearing surface to cooperate with the corrugated ring. The raceway grooves are annular grooves centered on the axis of the thrust bearing.

[0010] Optionally, in the above-mentioned thrust bearing, take any contact point between the corrugated ring and the raceway groove, the distance from the contact point to the axis of the rolling body is called distance M, and the distance from the contact point to the axis of the thrust bearing is called distance N. When the contact point is located on the shaft ring, the ratio of the distance M to the distance N is a first preset value; when the contact point is located on the seat ring, the ratio of the distance M to the distance N is a second preset value.

[0011] Optionally, in the above-mentioned thrust bearing, the contact points between the corrugated ring and the raceway groove are located on the groove slopes on both sides of the groove bottom of the raceway groove.

[0012] Optionally, in the above-mentioned thrust bearing, the contact point between the corrugated ring and the raceway groove is located on the groove bottom of the raceway groove.

[0013] Optionally, in the above-mentioned thrust bearing, the axis of the rolling element forms an acute angle with the axis of the thrust bearing.

[0014] Optionally, in the above-mentioned thrust bearing, in the contour line of the corrugated ring, the contact point with the groove slope of the raceway groove and the portion near it are circular arcs convex outward.

[0015] Optionally, in the above-mentioned thrust bearing, the acute angle formed by the tangent line at the contact point between the corrugated ring and the raceway groove and the axis of the thrust bearing is larger at a position farther from the axis of the thrust bearing in the radial direction of the thrust bearing than at a position closer to the axis of the thrust bearing.

[0016] Optionally, in the above-mentioned thrust bearing, the angle formed by two tangent lines on the contour line of any one of the corrugated rings at the two contact points on the same raceway groove is 30° to 150°.

[0017] Optionally, in the above thrust bearing, a gear is provided on the rolling element, and the axis of the gear coincides with the axis of the rolling element;

[0018] At least one of the shaft ring and the seat ring is provided with a gear ring on a pressure-bearing surface that meshes with the gear, and the axis of the gear ring coincides with the axis of the thrust bearing.

[0019] Optionally, in the above-mentioned thrust bearing, the thrust bearing is a sliding bearing, and the parts where the first annular groove and the second annular groove cooperate with each other are in surface contact.

[0020] Optionally, in the above-mentioned thrust bearing, the shaft ring includes a thrust washer, and the first annular groove is provided on the thrust washer;

[0021] The seat ring includes a mirror plate, and the second annular groove is provided on the mirror plate.

[0022] According to the above technical solution, in the thrust bearing provided by the present invention, a plurality of first annular grooves centered on the axis of the shaft ring are provided on the side of the shaft ring facing the seat ring, and a plurality of second annular grooves centered on the axis of the seat ring are provided on the side of the seat ring facing the shaft ring. Because the first annular grooves and the second annular grooves are directly interlaced with each other, or respectively cooperate with the annular protrusions on the circumferential surface of the rolling element through the rolling element, the first annular grooves and the second annular grooves directly or indirectly form a clamping connection in the radial direction of the thrust bearing, which can enable the thrust bearing to have a higher radial load capacity. Therefore, the thrust bearing provided by the present invention achieves a larger load capacity with a relatively simple structure. Due to its simple structure and high radial load capacity, the thrust bearing provided by the present invention is conducive to achieving a higher limit speed. BRIEF DESCRIPTION OF THE DRAWINGS

[0023] In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the following briefly introduces the drawings required for use in the embodiments or the description of the prior art. Obviously, the drawings described below are merely embodiments of the present invention. For ordinary technicians in this field, other drawings can be obtained based on the provided drawings without paying any creative work.

[0024] Figure 1 This is a perspective schematic diagram of the exploded parts of the thrust bearing provided in the first embodiment of the present invention;

[0025] Figure 2 1 is a schematic cross-sectional view of the exploded parts of the thrust bearing provided in the first embodiment of the present invention;

[0026] Figure 3 is a cross-sectional schematic diagram of a thrust bearing provided in Embodiment 1 of the present invention;

[0027] Figure 4 yes Figure 1 Top view of the middle race 2 and rolling element 3;

[0028] Figure 5 yes Figure 3 A magnified schematic diagram of point A in the middle;

[0029] Figure 6 is a partial cross-sectional schematic diagram of a thrust bearing provided in a second embodiment of the present invention;

[0030] Figure 7 yes Figure 6 A magnified schematic diagram of point B in the middle;

[0031] Figure 8 is a cross-sectional schematic diagram of a thrust bearing provided in a third embodiment of the present invention;

[0032] Figure 9is a partial cross-sectional schematic diagram of a thrust bearing provided in a fourth embodiment of the present invention;

[0033] Figure 10 This is a perspective schematic diagram of the exploded parts of the thrust bearing provided in the fifth embodiment of the present invention;

[0034] Figure 11 yes Figure 10 A three-dimensional schematic diagram of the shaft ring 1;

[0035] Figure 12 yes Figure 10 Schematic diagram of the assembly of the seat ring 2 and the rolling element 3;

[0036] Figure 13 yes Figure 10 A three-dimensional schematic diagram of the rolling element 3;

[0037] Figure 14 yes Figure 10 A front view of the rolling element 3 in FIG;

[0038] Figure 15 yes Figure 14 Right view;

[0039] Figure 16 1 is a cross-sectional schematic diagram of the exploded parts of the thrust bearing provided in the sixth embodiment of the present invention;

[0040] Figure 17 is a cross-sectional schematic diagram of a thrust bearing provided in a sixth embodiment of the present invention;

[0041] Figure 18 yes Figure 16 Bottom view of the center shaft ring 1;

[0042] Figure 19 is a cross-sectional schematic diagram of a thrust bearing provided in a seventh embodiment of the present invention;

[0043] Figure 20 1 is a perspective schematic diagram of the exploded parts of the thrust bearing provided by the seventh embodiment of the present invention;

[0044] Figure 21 yes Figure 20 Bottom view of the center shaft ring 1;

[0045] Figure 22 1 is a schematic cross-sectional view of the exploded parts of the thrust bearing provided in the eighth embodiment of the present invention;

[0046] Figure 23 is a cross-sectional schematic diagram of a thrust bearing provided in Example 8 of the present invention;

[0047] Figure 24 yes Figure 23 A partial enlarged view of

[0048] Figure 25 is a cross-sectional schematic diagram of a thrust bearing provided by a ninth embodiment of the present invention;

[0049] Figure 26 yes Figure 25 A partial enlarged view of .

[0050] The following are marked in the figure:

[0051] 1. Shaft washer; 101. Raceway groove; 102. Shaft hole; 103. Gear ring; 104. Slideway groove; 105. Oil groove;

[0052] 2. Seat ring; 201. Roller groove; 202. Bushing hole; 203. Gear ring; 204. Slide groove;

[0053] 3. Rolling element; 301. Corrugated ring; 302. Gear;

[0054] 4. Cage;

[0055] 5. Thrust pad;

[0056] 6. Mirror plate. DETAILED DESCRIPTION

[0057] To facilitate understanding, the present invention is further described below with reference to the accompanying drawings.

[0058] Example 1

[0059] See also Figures 1 to 5 , Figure 1 1 is a perspective schematic diagram of the exploded parts of the thrust bearing provided in the first embodiment of the present invention. Figure 2 1 is a cross-sectional schematic diagram of the exploded parts of the thrust bearing provided in the first embodiment of the present invention. Figure 3 is a cross-sectional schematic diagram of a thrust bearing provided in Embodiment 1 of the present invention, Figure 4 yes Figure 1 Top view of the middle race 2 and rolling element 3, Figure 5 yes Figure 3 Enlarged schematic diagram of point A in the middle.

[0060] The thrust bearing provided in the first embodiment of the present invention is a thrust roller bearing, comprising a shaft ring 1, a seat ring 2 and a rolling element 3. A plurality of corrugated rings 301 arranged along the axial direction of the rolling element 3 are provided on the circumferential surface of the rolling element 3. "Multiple" refers to more than two. The corrugated ring 301 is an annular protrusion centered on the axis of the rolling element 3. Both the shaft ring 1 and the seat ring 2 are provided with a plurality of raceway grooves on the pressure-bearing surface that cooperate with the corrugated ring 301. The raceway groove is an annular groove centered on the axis of the thrust bearing.

[0061] like Figures 1 to 3As shown, the rolling element 3 is located between the shaft ring 1 and the seat ring 2. A raceway groove 101 is provided on the shaft ring 1, and a raceway groove 201 is provided on the seat ring 2. After assembly, the corrugated ring 301 of the rolling element 3 is located in the raceway groove 101 and the raceway groove 201. Since the corrugated ring 301 and the raceway groove form a snap connection in the radial direction of the thrust bearing, the radial load-bearing capacity of the thrust bearing is relatively high, which is conducive to achieving a higher limit speed.

[0062] The middle of the shaft ring 1 is generally provided with an axis hole 102. The seat ring 2 is fixed on the base and is not in close contact with the rotating shaft of the load. In this embodiment, the seat ring 2 is provided with a sleeve hole 202 for the rotating shaft of the load to pass through.

[0063] like Figure 4 As shown, in order to ensure uniform force, multiple rolling bodies 3 are evenly arranged around the axis of the race 2.

[0064] like Figure 5 As shown, to minimize slippage between the rolling element 3 and the shaft ring 1, and between the rolling element 3 and the raceway 2, the contact point D between the corrugated ring 301 and the raceway groove must meet the following requirements: the distance from the contact point D to the axis X of the rolling element 3 is called distance M, and the distance from the contact point D to the axis Y of the shaft ring 1 is called distance N. For any contact point D between the corrugated ring 301 and the raceway groove, when the contact point D is on the shaft ring 1, the ratio of distance M to distance N is a first predetermined value. That is, for each contact point D on the shaft ring 1, the ratio of distance M to distance N is constant and equal to the first predetermined value. When the contact point D is on the raceway 2, the ratio of distance M to distance N is a second predetermined value. That is, for each contact point D on the raceway 2, the ratio of distance M to distance N is constant and equal to the second predetermined value. In practical applications, the first and second predetermined values can be equal.

[0065] Example 2

[0066] The only difference between the second embodiment and the first embodiment is that the position of the contact point D on the raceway groove is different. Figure 6 and Figure 7 , Figure 6 is a partial cross-sectional schematic diagram of a thrust bearing provided in the second embodiment of the present invention, Figure 7 yes Figure 6 The enlarged schematic diagram of point B in the middle is compared Figure 5 and Figure 6 It can be seen that in the first embodiment, the contact point D between the corrugated ring 301 and the raceway groove is located on the groove bottom of the raceway groove, while in the second embodiment, the contact point D is located on the groove slopes on both sides of the groove bottom of the raceway groove.

[0067] As described in Example 1, for each contact point D, the ratio of the distance M to the distance N is constant. Therefore, the contact points D located on the same side of the axis X of the rolling element 3 are located on the same straight line. Furthermore, since the contact points D are located on the groove slopes on both sides of the groove bottom of the raceway groove, it is not difficult to understand that, in the radial section of the thrust bearing, the line connecting the contact points D passes through the groove portion of the raceway groove and the raised portion between the raceway grooves. In order to make the material cross-sectional area of the rolling element 3, the shaft ring 1 and the seat ring 2 that resists radial extrusion force equal, the total length of the line connecting the contact points D passing through the groove portion of the raceway groove should be equal to the total length of the line connecting the contact points D passing through the raised portion between the raceway grooves.

[0068] like Figure 7 As shown, in the outline of the corrugated ring 301 , the contact point with the groove slope of the raceway groove and the portion nearby can be an arc convex outward.

[0069] Furthermore, the cross-sectional shape of the corrugated ring 301 can be formed into various shapes as needed. Its technical solution is similar to that of a thread profile, and can be formed into a Gothic profile, an arc profile, an involute profile, a triangular profile, a trapezoidal profile, etc. Similarly, the contour line of the slope of the raceway groove can be a straight line or a curved line such as an arc line.

[0070] like Figure 6 As shown, in the second embodiment, the angle bisector of the angle formed by two tangent lines at two contact points D on the contour line of any corrugated ring 301 located on the same raceway groove is perpendicular to the axis X of the rolling element 3, and the angle formed by the above two tangent lines is generally 30° to 150°, for example, 90°.

[0071] Example 3

[0072] See also Figure 8 , Figure 8 : is a cross-sectional schematic diagram of a thrust bearing provided by embodiment 3 of the present invention. Embodiment 3 is an improvement made on the basis of embodiment 1 or embodiment 2. Figure 8 and Figure 3 As can be seen, in the third embodiment, there are two seat rings 2, and the upper and lower surfaces of the shaft ring 1 are both provided with raceway grooves 101, so that there are two layers of rolling elements 3. Of course, in other embodiments, the rolling elements 3 can also be provided with more layers, as long as the number of shaft rings 1 is increased accordingly.

[0073] like Figure 8 As shown, the third embodiment provides a bidirectional thrust bearing, in which both sides of the shaft ring 1 have seat rings 2, so that the forces in both directions along the axial direction of the load can be transmitted from the shaft ring 1 to the seat ring 2 through the rolling element 3, and then to the base.

[0074] Similarly, the bidirectional thrust bearing may also be composed of two shaft rings 1 and a seat ring 2, with the shaft ring 1 and the seat ring 2 supported and force transmitted by rolling elements 3.

[0075] Example 4

[0076] Depend on Figure 4 It can be seen that the uniform arrangement of multiple rolling elements 3 can make the force uniform. The fourth embodiment mainly provides a method for maintaining the relative position relationship between the rolling elements 3, such as Figure 9 As shown, the rolling elements 3 are arranged in the retaining frame 4 , and the retaining frame 4 fixes the relative positions of the rolling elements 3 .

[0077] In order to make the rolling element 3 and the retaining frame 4 match more precisely, mutually matching protrusions and recesses can be made on the rolling element 3 and the retaining frame 4. With the protrusions and recesses fitting together, the rolling element 3 can be accurately installed in the retaining frame 4.

[0078] Example 5

[0079] The fifth embodiment provides another method for maintaining the relative position relationship between the rolling elements 3, as shown in FIG. 10 to FIG. Figure 15 , Figure 10 1 is a perspective schematic diagram of the exploded parts of the thrust bearing provided by the fifth embodiment of the present invention. Figure 11 yes Figure 10 A three-dimensional schematic diagram of the shaft ring 1, Figure 12 yes Figure 10 The assembly diagram of the seat ring 2 and the rolling element 3, Figure 13 yes Figure 10 A three-dimensional schematic diagram of the rolling element 3 in FIG. Figure 14 yes Figure 10 The front view of the rolling element 3 in FIG. Figure 15 yes Figure 14 Right view of .

[0080] In Example 5, a gear 302 is provided on the rolling body 3, and the axis of the gear 302 coincides with the axis of the rolling body 3. Both the shaft ring 1 and the seat ring 2 are provided with a gear ring on the pressure bearing surface that meshes with the gear 302, and the axis of the gear ring coincides with the axis of the shaft ring 1.

[0081] like Figure 10 and Figure 11 As shown, a gear ring 103 is provided on the shaft ring 1, a gear ring 203 is provided on the seat ring 2, and the gear 302 on the rolling element 3 is meshed with the gear ring 103 and the gear ring 203 at the same time.

[0082] In practical applications, the gear 302 can be constructed at any position on the rolling element 3, but the preferred solution is to construct the gear 302 at both ends of the rolling element 3, such as Figure 13 and Figure 14 shown.

[0083] As described in Example 1, to minimize slippage, for each contact point D (the contact point between the corrugated ring 301 and the raceway groove), the ratio of distance M (the distance from contact point D to the axis X of the rolling element 3) to distance N (the distance from contact point D to the axis Y of the shaft ring 1) is constant and is a preset value. Accordingly, in Example 5, for each contact point between the gear 302 and the ring gear, the ratio of the distance from the axis X to the distance from the axis Y is also the preset value.

[0084] It should be understood that in other embodiments, a gear ring meshing with the gear 302 may be provided on only one of the shaft ring 1 and the seat ring 2 , which can also maintain the relative positions of the rolling elements 3 .

[0085] Example 6

[0086] See also Figures 16 to 18 , Figure 16 FIG1 is a cross-sectional schematic diagram of the exploded parts of the thrust bearing provided in the sixth embodiment of the present invention. Figure 17 is a cross-sectional schematic diagram of a thrust bearing provided in Example 6 of the present invention, Figure 18 yes Figure 16 Bottom view of the center ring 1.

[0087] The thrust bearing provided in the sixth embodiment of the present invention is a sliding bearing, comprising a shaft ring 1 and a seat ring 2. The shaft ring 1 is provided with a plurality of first corrugated rings on the pressure-bearing surface, and the seat ring 2 is provided with a plurality of second corrugated rings that cooperate with the first corrugated rings on the pressure-bearing surface. The first corrugated ring is an annular groove centered on the axis of the shaft ring 1 (i.e., the axis of the thrust bearing), and the second corrugated ring is an annular groove centered on the axis of the seat ring 2 (i.e., the axis of the thrust bearing). The first corrugated ring and the second corrugated ring are directly staggered and matched, and the mutually matched parts of the two are in surface contact.

[0088] like Figure 16 and Figure 17 As shown, in this embodiment, the corrugated rings are formed alternately on both the shaft ring 1 and the seat ring 2. Slide grooves 104 are formed between adjacent first corrugated rings on the shaft ring 1, and slide grooves 204 are formed between adjacent second corrugated rings on the seat ring 2. Because the first and second corrugated rings are staggered, the slide grooves 104 on the shaft ring 1 and the slide grooves 204 on the seat ring 2 are staggered. The mating first and second corrugated rings form a snap-fit connection in the radial direction of the thrust bearing, resulting in a high radial load capacity for the thrust bearing, which is conducive to achieving a high limiting speed.

[0089] like Figure 18As shown, for the convenience of lubrication, an oil groove 105 is provided on the shaft ring 1. Of course, an oil groove can also be provided on the seat ring 2.

[0090] Example 7

[0091] See also Figure 20 and Figure 21 , Figure 20 1 is a perspective schematic diagram of the exploded parts of the thrust bearing provided by the seventh embodiment of the present invention. Figure 21 yes Figure 20 Bottom view of the center ring 1.

[0092] The thrust bearing provided in Example 7 is also a sliding bearing, and the only difference from Example 6 is that the shaft ring 1 includes a thrust washer 5, and the first corrugated ring is arranged on the thrust washer 5; the seat ring 2 includes a mirror plate 6, and the second corrugated ring is arranged on the mirror plate 6.

[0093] Example 8

[0094] See also Figures 22 to 24 , Figure 22 FIG1 is a schematic cross-sectional view of the exploded parts of the thrust bearing provided in the eighth embodiment of the present invention. Figure 23 is a cross-sectional schematic diagram of a thrust bearing provided in Example 8 of the present invention, Figure 24 yes Figure 23 A partial enlarged view of .

[0095] and Figure 5 Similar to the structure of the first embodiment shown, in the eighth embodiment, to minimize slippage between the rolling element 3 and the shaft ring 1, and between the rolling element 3 and the raceway 2, the contact points between the corrugated ring 301 and the raceway groove must meet the following requirements: the distance from the contact point to the axis of the rolling element 3 is called distance M, and the distance from the contact point to the axis of the shaft ring 1 is called distance N. For any contact point between the corrugated ring 301 and the raceway groove, when the contact point is on the shaft ring 1, the ratio of distance M to distance N is a third preset value. That is, for each contact point on the shaft ring 1, the ratio of distance M to distance N is constant and equal to the third preset value. When the contact point is on the raceway 2, the ratio of distance M to distance N is a fourth preset value. That is, for each contact point on the raceway 2, the ratio of distance M to distance N is constant and equal to the fourth preset value. In practical applications, the third and fourth preset values can be equal.

[0096] Depend on Figure 5 It can be seen that in the first embodiment, the angles formed between the groove slopes of all the raceway grooves and the axis of the thrust bearing are the same, while the curvature radii of the contour lines of the various corrugated rings 301 on the same rolling element 3 are different.

[0097] like Figure 24As shown, unlike the first embodiment, in the eighth embodiment, the curvature radius of the contour lines of all the corrugated rings 301 is the same, but the angles formed between the groove slopes of each raceway groove and the axis of the thrust bearing are different. The purpose is to adjust the position of the contact point by adjusting the angle of the groove slope when manufacturing the raceway groove to ensure that all contact points meet the anti-slip requirements mentioned above.

[0098] Embodiment 9

[0099] See also Figure 25 and Figure 26 , Figure 25 is a cross-sectional schematic diagram of a thrust bearing provided by Embodiment 9 of the present invention, Figure 26 yes Figure 25 A partial enlarged view of .

[0100] In Example 9, the contact points between the corrugated ring of the rolling element 3 and the raceway grooves of the shaft ring 1 and the seat ring 2 also meet the anti-slip requirements mentioned above. However, unlike Example 1 and Example 8, the axis of the rolling element 3 in Example 9 is not perpendicular to the axis of the thrust bearing, but forms an acute angle with it.

[0101] It is easy to understand that in the thrust roller bearings provided in the aforementioned embodiments, the direction of the tangent at the contact point between the rolling element's corrugated ring and the raceway groove significantly influences the distribution of the thrust bearing's load capacity in both the forward and lateral directions. "Forward" refers to the axial direction of the thrust bearing, while "lateral" refers to the radial direction of the thrust bearing. The larger the acute angle formed between the tangent at the contact point between the corrugated ring and the raceway groove and the axis of the thrust bearing, the greater the forward force the bearing can withstand, while also reducing the lateral force it can withstand. In practical applications, the aforementioned acute angle can be designed to increase radially as the distance from the thrust bearing axis increases. In other words, the acute angle formed by the tangent at the contact point between the corrugated ring and the raceway groove and the axis of the thrust bearing increases at locations farther from the axis than at locations closer to the axis. This allows for a more efficient distribution of the load capacity at each corrugated ring. In addition, the angle formed by two tangent lines at two contact points on the same raceway groove on the contour line of any corrugated ring is generally 30° to 150°.

[0102] The above description of the disclosed embodiments is intended to enable one skilled in the art to implement or use the present invention. Various modifications to the embodiments will be readily apparent to one skilled in the art, and the general principles defined herein may be implemented in other embodiments without departing from the spirit or scope of the present invention. Therefore, the present invention is not limited to the embodiments shown herein but is to be construed in the widest manner consistent with the principles and novel features disclosed herein.

Claims

1. A thrust bearing comprising a shaft ring (1) and a seat ring (2), characterized in that: A plurality of first annular grooves centered on the axis of the thrust bearing are provided on a side of the shaft ring (1) facing the seat ring (2); A plurality of second annular grooves centered on the axis of the thrust bearing are provided on a surface of the seat ring (2) facing the shaft ring (1); The first annular groove and the second annular groove are directly interlaced with each other, or are respectively matched with the annular protrusions on the circumference of the rolling body (3) through the rolling body (3); The thrust bearing is a thrust roller bearing, comprising a rolling element (3), a plurality of corrugated rings (301) arranged along the axial direction of the rolling element (3) are provided on the circumferential surface of the rolling element (3), and the corrugated ring (301) is an annular protrusion centered on the axis of the rolling element (3); the shaft ring (1) and the seat ring (2) are both provided with a plurality of raceway grooves on the pressure-bearing surface that cooperate with the corrugated ring (301), and the raceway groove is an annular groove centered on the axis of the thrust bearing; taking any contact point between the corrugated ring (301) and the raceway groove, the distance from the contact point to the axis of the rolling element (3) is called distance M, and the distance from the contact point to the axis of the thrust bearing is called distance N, and when the contact point is located on the shaft ring (1), the ratio of the distance M to the distance N remains unchanged, and both are first preset values; When the contact point is located on the seat ring (2), the ratio of the distance M to the distance N remains unchanged and is a second preset value; The axis of the rolling element (3) forms an acute angle with the axis of the thrust bearing.

2. The thrust bearing according to claim 1, characterized in that The contact points between the corrugated ring (301) and the raceway groove are located on the groove slopes on both sides of the groove bottom of the raceway groove.

3. The thrust bearing according to claim 2, characterized in that: In the contour line of the corrugated ring (301), the contact point with the groove slope of the raceway groove and the portion nearby are arcs convex outwards.

4. The thrust bearing according to claim 3, characterized in that: In the radial direction of the thrust bearing, the acute angle formed by the tangent of the corrugated ring (301) at the contact point with the raceway groove and the axis of the thrust bearing is larger than that of the tangent at the contact point with the axis of the thrust bearing.

5. The thrust bearing according to claim 4, characterized in that: The angle formed by two tangent lines at two contact points on the same raceway groove on the contour line of any one of the corrugated rings (301) is 30° to 150°.

6. The thrust bearing according to any one of claims 1 to 5, characterized in that: A gear (302) is provided on the rolling body (3), and the axis of the gear (302) coincides with the axis of the rolling body (3); At least one of the shaft ring (1) and the seat ring (2) is provided with a gear ring on the pressure-bearing surface, which is engaged with the gear (302), and the axis of the gear ring coincides with the axis of the thrust bearing; At each contact point between the gear (302) and the gear ring (1), the ratio of the distance between each contact point and the axis of the rolling element (3) to the distance between each contact point and the axis of the thrust bearing is a preset value.

7. The thrust bearing according to claim 1, wherein: The thrust bearing is a sliding bearing, and the first annular groove and the second annular groove cooperate with each other in a surface contact manner.

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