CN117515048A - Bearing assembly - Google Patents

Abstract

The present invention relates to a bearing assembly. The bearing assembly includes an inner race, an outer race, and a pressure plate, the pressure plate including a mounting hole and one or more first bosses extending radially inward from an inner periphery of the mounting hole, respectively, the outer race including an annular mounting groove formed on a radially outer side of the axial end portion and one or more recesses penetrating from an end face of the axial end portion to the mounting groove, respectively. The outer race further includes two second bosses formed on a radial bottom surface of the mounting groove, each first boss being insertable into the mounting groove beyond the constraint section through a respective recess, and one of the one or more first bosses inserted into the mounting groove being capable of entering the constraint section through elastic deformation past one of the two second bosses, thereby defining a predetermined range of relative rotation between the outer race and the pressure plate within which each first boss is not circumferentially aligned with the respective recess. The bearing assembly of the present invention is easy to install.

Description

Bearing assembly

Technical Field

The invention relates to the technical field of bearings. In particular, the present invention relates to a bearing assembly having a platen.

Background

Deep groove ball bearings with pressure plates are typically used in gearboxes, the function of the pressure plates being to mount the deep groove ball bearings to the gearbox housing. The pressing plate is assembled with the outer ring of the bearing in a press fit mode, and after the pressing plate is assembled in place, the pressing plate is connected with the outer ring in a loose fit mode and can freely rotate relative to the outer ring along the circumferential direction.

A common assembly method is currently disclosed in patent literature such as CN 106460938B. Wherein, be formed with circular mounting hole on the clamp plate, be formed with three bellying along circumference evenly distributed on the inner periphery of mounting hole. When the pressing plate is assembled on the outer ring, the protruding parts of the pressing plate need to be pressed into the annular mounting groove of the outer ring one by one through elastic deformation. When all the protruding parts are pressed into the mounting grooves, the material of the protruding parts can be restored to form axial constraint, and the pressing plate and the outer ring are allowed to rotate relatively through sliding clamping of the protruding parts and the mounting grooves while the pressing plate and the bearing are prevented from being separated.

The above-described mounting method has a disadvantage in that the protruding portion of the pressing plate is deformed when being pressed into the mounting groove, and the deformation undergone by the last pressed protruding portion is particularly large, which may cause breakage of the protruding portion, whereby various problems may occur. First, the fracture surface of the boss may generate some debris that contaminates the bearing. Meanwhile, as radial positioning between the pressing plate and the outer ring is realized by at least three protruding parts, under the condition that part of protruding parts are missing, the relative positions between the pressing plate and the outer ring deviate, so that the pressing plate is clamped by the outer ring. In this case, the pressing plate is also easily detached from the outer race and falls. Finally, due to the problems of elliptical deformation of the outer ring after heat treatment, even if the sizes of the bulges after press fitting are consistent, partial point constraint is poor, so that the pressing plate falls off. Therefore, the stability requirements of this structure for heat treatment are also very high. In order to reduce the falling rate, the matching with the inner diameter of the pressing plate can be ensured only by turning the step surface after heat treatment, so that the processing cost is greatly increased.

Disclosure of Invention

Accordingly, it is a technical problem to be solved by the present invention to provide an improved bearing assembly.

The above technical problem is solved by a bearing assembly according to the present invention. The bearing assembly includes an inner ring, an outer ring mounted on a radially outer side of the inner ring, and a pressing plate mounted on the radially outer side of the outer ring, the pressing plate including a mounting hole and one or more first protrusions extending radially inward from an inner periphery of the mounting hole, respectively, the outer ring including an annular mounting groove formed on the radially outer side of the axial end portion and one or more recesses penetrating through the mounting groove from an end face of the axial end portion, respectively, each of the first protrusions being insertable into the mounting groove through a corresponding recess, such that the outer ring is rotatably mounted in the mounting hole. Wherein the outer race further comprises two second bosses formed on a radial bottom surface of the mounting groove, the two second bosses being circumferentially spaced apart to define a restraining section of the mounting groove therebetween, each first boss being insertable into the mounting groove beyond the restraining section through a respective recess, and one of the one or more first bosses inserted into the mounting groove being capable of entering the restraining section through elastic deformation past one of the two second bosses to define a predetermined relative rotational range between the outer race and the pressure plate through the two second bosses within which each first boss is not circumferentially aligned with the respective recess. The rotation range of the pressing plate with respect to the outer ring is restricted by two second protrusions formed in the mounting groove such that the first protrusions on the pressing plate cannot be aligned with the recesses on the outer ring after the mounting is completed, thereby effectively preventing the pressing plate from being separated from the outer ring. Meanwhile, in the installation process, the first protruding part can pass through the second protruding part and enter the constraint section without applying larger external force, so that the deformation of the protruding part is small, and the risk of damaging the protruding part can be reduced.

According to a preferred embodiment of the invention, when one of the one or more first protrusions enters the constraining section to define the predetermined range of relative rotation, the other of the one or more first protrusions may be located outside the constraining section. That is, only one first boss needs to be elastically deformed into the restraining section, which makes the installation process more convenient.

According to a further preferred embodiment of the invention, the radial height of each second projection may decrease from the middle to both sides in a cross section perpendicular to the axial direction. This results in the circumferential sides of the second projection forming an inclined slope which facilitates guiding the first projection past the second projection by elastic deformation into or out of the constraining section.

According to a further preferred embodiment of the invention, in a cross section perpendicular to the axial direction, the slope of the side of each second projection facing the interior of the restriction section may be greater than the slope of the side facing the exterior of the restriction section. This makes it easier for the first boss to pass over the second boss into the restraining section during installation, and less easy for the second boss to pass over out of the restraining section in the installed state.

According to another preferred embodiment of the invention, each second projection may have a profile symmetrical about a circumferential midpoint in a cross section perpendicular to the axial direction. The shape is convenient to process, and is beneficial to reducing the production cost.

According to another preferred embodiment of the present invention, each of the second protrusions may have an arc-shaped profile protruding toward the radially outer side in a cross section perpendicular to the axial direction. This shape facilitates the first boss to pass over the second boss and may reduce stress concentrations.

According to another preferred embodiment of the present invention, in a cross section perpendicular to the axial direction, the radially inner end face of each first boss may have an arc-shaped profile recessed toward the radially outer side. The inboard profile of each first lobe is thereby adapted to the outboard profile of the second lobe to facilitate guiding the first lobe past the second lobe.

According to another preferred embodiment of the present invention, the circumferential length of each first protrusion may be smaller than the circumferential length of the corresponding recess. This allows the first boss to be easily inserted into the mounting groove through the recess.

According to another preferred embodiment of the invention, the circumferential angle between the edges of the two second protrusions facing the constraining section may be 60 degrees. This provides a practically advantageous range of relative rotation.

Drawings

The invention is further described below with reference to the accompanying drawings. Like reference numerals in the drawings denote functionally identical elements. Wherein:

FIG. 1 illustrates a front view of a bearing assembly according to an exemplary embodiment of the present invention;

FIG. 2 illustrates a perspective view of a bearing assembly according to an exemplary embodiment of the present invention;

FIG. 3 illustrates a perspective view of an outer race of a bearing assembly according to an exemplary embodiment of the present invention;

FIG. 4 illustrates a cross-sectional view of an outer race of a bearing assembly according to an exemplary embodiment of the present invention; and

fig. 5 illustrates a rotational state schematic of a bearing assembly according to an exemplary embodiment of the present invention.

Detailed Description

Specific embodiments of a bearing assembly according to the present invention will be described below with reference to the accompanying drawings. The following detailed description and the accompanying drawings are provided to illustrate the principles of the invention and not to limit the invention to the preferred embodiments described, the scope of which is defined by the claims.

According to an embodiment of the present invention, a bearing assembly is provided. The bearing assembly mainly comprises a bearing device and a pressing plate. Fig. 1 and 2 show a front view and a perspective view, respectively, of a bearing assembly according to an exemplary embodiment of the present invention. As shown in fig. 1 and 2, the bearing device may be a common various types of bearings, such as a deep groove ball bearing, etc., which includes an outer race 10, an inner race 20, and a plurality of rolling bodies. The outer ring 10 and the inner ring 20 are respectively formed in annular structures, and the outer ring 10 is coaxially arranged radially outside the inner ring 20. A plurality of rolling bodies are circumferentially distributed between the outer ring 10 and the inner ring 20 and are capable of rolling around a central axis of the bearing device along an inner side wall of the outer ring 10 and an outer side wall of the inner ring 20, thereby allowing the outer ring 10 and the inner ring 20 to relatively rotate around the central axis.

The pressure plate 30 is formed in a substantially flat plate-like structure, and when the pressure plate 30 is mounted with the bearing device, the plane of extension of the pressure plate 30 is substantially perpendicular to the central axis of the bearing device. The pressing plate 30 is formed with a circular mounting hole into which the bearing device can be placed such that the pressing plate 30 is mounted radially outside the outer ring 10.

Fig. 3 shows a perspective view of the outer ring 10 of the bearing arrangement. As shown in fig. 2, the outer race 10 has two axially opposite axial ends. An annular mounting groove 11 is formed on the radially outer side of one axial end portion of the outer ring 10. The mounting groove 11 is formed by the radially outer side surface of the outer ring 10 being recessed toward the radially inner side at a position near the axial end surface. In a section through the central axis, the mounting groove 11 may have, for example, a rectangular shape.

As shown in fig. 1 and 2, the pressing plate 30 includes one or more first protrusions 31 formed in the mounting hole. When there are a plurality of first protrusions 31, these first protrusions 31 are circumferentially spaced apart. Each of the first bosses 31 extends radially inward from an inner peripheral edge of the mounting hole, respectively. When the pressure plate 30 is mounted radially outside the bearing device, each of the first protrusions 31 is inserted radially into the mounting groove 11 of the outer ring 10, the first protrusions 31 being axially constrained by the side walls of the mounting groove 11, thereby defining the relative axial position between the pressure plate 30 and the outer ring 10; at the same time, the first boss 31 is loosely fitted with the mounting groove 11 with a gap therebetween, thereby allowing relative rotation between the pressing plate 30 and the outer race 10. The outer race 10 is thereby rotatably mounted in the mounting bore.

As shown in fig. 1 to 3, one or more notches 12 are also formed on the radially outer side of the outer ring 10 corresponding to the first boss 31 on the pressing plate 30. When a plurality of notches 12 are present, the notches 12 are also circumferentially spaced apart. Each recess 12 is recessed from a radially outer side face of an axial end portion where the mounting groove 11 is located toward a radially inner side, and penetrates substantially axially from an end face of the axial end portion (i.e., an axial end face near the mounting groove 11) to the mounting groove 11. The first protrusions 31 on the pressing plate 30 and the recesses 12 on the outer ring 10 correspond in number and position, respectively. That is, the number of first protrusions 31 is equal to the number of recesses 12, each first protrusion 31 corresponds to a corresponding recess 12, and each first protrusion 31 can be aligned with a corresponding recess 12 in the circumferential direction when the pressure plate 30 and the outer race 10 are located at a predetermined circumferentially opposite position with respect to each other. At this time, each first boss 31 may pass through the corresponding recess 12 in the axial direction so as to enter the inside of the mounting groove 11. Preferably, in a cross section perpendicular to the axial direction, the recess 12 may be formed as a substantially rectangular recess. Preferably, the circumferential length of each first protrusion 31 may be smaller than the circumferential length of the corresponding recess 12, such that the first protrusions 31 may pass through the recess 12 without elastic deformation.

Preferably, a plurality of first protrusions 31 and a corresponding plurality of recesses 12 may be provided. These first projections 31 and recesses 12 may in particular be evenly distributed in the circumferential direction. In general, three first protrusions 31 and three recesses 12 may be provided. In the case of uniform distribution, adjacent first protrusions 31 or adjacent recesses 12 are spaced apart by a circumferential angle of 120 degrees.

Fig. 4 shows a cross section of the outer ring 10 perpendicular to the axial direction. As shown in fig. 4, two second protrusions 13 are also formed on the radial bottom surface of the mounting groove 11 of the outer ring 10. Each of the second protrusions 13 protrudes from the radial bottom surface of the mounting groove 11 toward the radial outside by a radial height smaller than the radial depth of the mounting groove 11, and thus does not protrude outside the mounting groove 11. The two second bosses 13 are circumferentially spaced apart so as to define therebetween a constraint section R of the mounting groove 11. The constraint segment R is a segment having a circumferential angle smaller than 180 degrees.

All the second projections 13 are circumferentially offset from the notches 12 and are circumferentially outside the constraint segment R. After all the first projections 31 of the pressure plate 30 have been inserted into the mounting groove 11 through the respective recesses 12, all the first projections 31 are initially outside the restraining section R and are circumferentially offset from the second projections 13, so that the first projections 31 can initially be moved circumferentially in the mounting groove 11 so that the pressure plate 30 can be rotated relative to the outer ring 10. When rotated to a certain position, one of the first protrusions 31 will first reach the position of one of the second protrusions 13. The radial height of the first 31 and second 13 projections is such that both need to be elastically deformed to allow the first projection 31 to pass circumferentially over the second projection 13 and into the restriction R. Such elastic deformation may be achieved by applying an external force to the pressing plate 30 and/or the outer ring 10 during installation. Fig. 5 shows a process in which the first convex portion 31 passes over the second convex portion 13 by elastic deformation. After the first boss 31 enters the restriction section R, if no external force is applied, the first boss 31 will be restricted within the restriction section R by the two second bosses 13, thereby defining a predetermined relative rotation range between the outer race 10 and the platen press 30. Each of the first protrusions 31 cannot be aligned with the corresponding recess 12 in the circumferential direction within a predetermined relative rotation range, and thus the first protrusions 31 cannot be disengaged from the mounting groove 11 through the corresponding recess 12, thereby ensuring a stable connection state of the pressure plate 30 with the outer race 10.

In the case where there are a plurality of first protrusions 31, after one first protrusion 31 enters the restriction section R, the allowable rotation range between the pressing plate 30 and the outer ring 10 is limited by the first protrusion 31 and the two second protrusions 13 within the above-described predetermined relative rotation range. At this time, in this rotation range, any other first boss 31 is always located outside the restriction section R without reaching any second boss 13, and thus relative rotation between the pressure plate 30 and the outer ring 10 is not hindered. In other words, at most one first projection 31 is located in the constraint segment R at any relative rotational position between the pressure plate 30 and the outer ring 10.

As shown in fig. 4, preferably, in the case where there are three first protrusions 31 uniformly distributed, the restriction section R may define the allowable rotation range between the pressing plate 30 and the outer race 10 as 60 degrees. Specifically, the allowable rotation range is a circumferential angle between edges of the two second bosses 13 toward the restricting section R. It is also preferred that the circumferential angle between the two second protrusions 13 at both ends of the restriction section R and the corresponding recesses 12 at both sides may also be equal.

As shown in the right-hand enlarged view of fig. 4, the second boss 13 is preferably formed as a boss (radially outward boss) whose radial height gradually decreases from the middle to both sides, for example, a boss having a triangular profile or an arc-shaped profile in a cross section perpendicular to the axial direction. A second boss having an arcuate profile is generally preferred for reducing stress concentrations and the like. In a preferred embodiment, in a cross section perpendicular to the axial direction, the slope of the side of the second protrusion 13 facing the inside of the restriction section R may be greater than the slope of the side facing the outside of the restriction section R, which makes it easier for the first protrusion 31 to enter the restriction section R beyond the second protrusion 13 than to leave the restriction section R, which not only facilitates the mounting of the platen 30, but also may reduce the risk of the platen 30 falling off in the mounted state. Alternatively, in another preferred embodiment, the second projection 13 may also have a profile symmetrical about the circumferential midpoint in a cross section perpendicular to the axial direction. On the one hand, the contour is easier to process, which is beneficial to reducing the production cost, and on the other hand, since no significant circumferential load needs to be born between the pressing plate 30 and the outer ring 10 in the working state, the risk of the pressing plate 30 and the outer ring 10 being accidentally separated under the action of external force is also lower.

In the case of the second projection 13 having an arcuate profile, the radially inner end face of the first projection 31 also preferably has an arcuate profile recessed toward the radially outer side in a cross section perpendicular to the axial direction. The first and second protrusions 31 and 13 are in contact with each other through the arc surfaces, and stress concentration phenomenon generated when the first and second protrusions are in contact can be reduced, thereby reducing the risk of damaging the protrusions.

The bearing assembly provided by the invention can effectively simplify the assembly process of the pressing plate and the bearing device, reduce the damage risk and simultaneously does not influence the rotation flexibility between the pressing plate and the outer ring. This greatly improves the reliability of the product. Meanwhile, the bearing assembly is simple in structure, easy to process and low in production cost.

While possible embodiments are exemplarily described in the above description, it should be understood that there are numerous variations of the embodiments still through all known and furthermore easily conceivable combinations of technical features and embodiments by the skilled person. It should also be appreciated that the exemplary embodiment or exemplary embodiments are only examples, and are not intended to limit the scope, applicability, or configuration of the invention in any way. The technical teaching for converting at least one exemplary embodiment is provided more in the foregoing description to the skilled person, wherein various changes may be made without departing from the scope of the claims, in particular with regard to the function and structure of the components.

Reference numeral table

10. Outer ring

11. Mounting groove

12. Recess (es)

13. Second protruding part

20. Inner ring

30. Pressing plate

31. A first protruding part

R constraint segment

Claims (9)

1. A bearing assembly comprising an inner ring (20), an outer ring (10) and a pressing plate (30), the outer ring (10) being mounted radially outwardly of the inner ring (20), the pressing plate (30) being mounted radially outwardly of the outer ring (10), the pressing plate (30) comprising a mounting hole and one or more first protrusions (31) extending radially inwardly from an inner periphery of the mounting hole, respectively, the outer ring (10) comprising an annular mounting groove (11) formed on the radially outwardly of an axial end portion and one or more recesses (12) penetrating the mounting groove (11) from an end face of the axial end portion, respectively, each first protrusion (31) being insertable into the mounting groove (11) through a corresponding recess (12) such that the outer ring (10) is rotatably mounted in the mounting hole,

it is characterized in that the method comprises the steps of,

the outer ring (10) further comprises two second protrusions (13) formed on a radial bottom surface of the mounting groove (11), the two second protrusions (13) being circumferentially spaced apart so as to define a constraint zone (R) of the mounting groove (11) therebetween, each first protrusion (31) being insertable into the mounting groove (11) outside the constraint zone (R) through a respective recess (12), and one of the one or more first protrusions (31) inserted into the mounting groove (11) being capable of entering the constraint zone (R) through elastic deformation beyond one of the two second protrusions (13), such that a predetermined relative rotational range between the outer ring (10) and the pressure plate (30) is defined by the two second protrusions (13), within which predetermined relative rotational range each first protrusion (31) is not circumferentially alignable with the respective recess (12).

2. Bearing assembly according to claim 1, wherein when one of the one or more first protrusions (31) enters the constraint segment (R) defining the predetermined relative rotation range, the other of the one or more first protrusions (31) is located outside the constraint segment (R).

3. Bearing assembly according to claim 2, wherein the radial height of each second projection (13) decreases from the middle to both sides in a cross section perpendicular to the axial direction.

4. A bearing assembly according to claim 3, characterized in that in a cross section perpendicular to the axial direction, the slope of the side of each second projection (13) facing the inside of the constraint segment (R) is greater than the slope of the side facing the outside of the constraint segment (R).

5. A bearing assembly according to claim 3, wherein each second projection (13) has a profile symmetrical about a circumferential midpoint in a cross-section perpendicular to the axial direction.

6. A bearing assembly according to claim 3, wherein each second projection (13) has an arcuate profile projecting radially outwards in a cross-section perpendicular to the axial direction.

7. Bearing assembly according to claim 6, wherein in a cross section perpendicular to the axial direction, the radially inner end face of each first projection (31) has an arc-shaped profile recessed towards the radially outer side.

8. Bearing assembly according to claim 1, wherein the circumferential length of each first projection (31) is smaller than the circumferential length of the corresponding recess (12).

9. Bearing assembly according to any one of claims 1 to 8, wherein the circumferential angle between the edges of the two second protrusions (13) facing the constraint segment (R) is 60 degrees.