Bearing

Abstract

The present disclosure proposes a bearing comprising a bearing body (2) and a bearing cap (1), wherein the bearing body comprises a radially bearing inner race (22) and a radially bearing outer race (21), one of the bearing inner race (22) and the bearing outer race (21) being a rotating race and the other being a stationary race; the bearing cap has an annular shape and is configured to fit with the bearing body such that a bearing cavity is formed between the bearing cap and the bearing body. The bearing cap (1) includes: a first section (11) located on a side of the bearing cap adjacent to the rotating race, the first section being made of metal, the first section (11) being fitted with the rotating race; and a second section (12) located on a side of the bearing cap adjacent to the stationary race, the second section (12) being made of a non-metal. The second section (12) is press-fitted with the stationary race, and a material of which the stationary race is made has a modulus of elasticity greater than 600 times of a modulus of elasticity of the non-metal material of which the second section is made.

Description

BearingTECHNICAL FIELD

[0001] The present disclosure relates to the field of bearings, in particular to a bearing having a bearing cap.BACKGROUND

[0002] Bearings have been widely used in more and more fields, and demands on the bearings have been increased, for example, more and more bearings have been required to be provided with bearing caps to avoid intrusion of external contaminants and leakage of lubricant. Whereas the conventional metal bearing cap is mounted between the inner race and the outer race of the bearing by press-fitting, which easily causes deformation of the outer race, particularly for a thin-walled bearing, since its outer race is thin, the outer race tends to be excessively deformed after mounting the bearing cap with high rigidity, affecting the use of the bearing.

[0003] Although rubber bearing caps already exist, such a rubber bearing cap is easily deformed by heat, and thus its rubber section adjacent to the bearing inner race may cause friction with the bearing inner race, making the sealing performance unstable and affecting the bearing rotation performance, so that rubber bearing cap is not suitable for high-temperature and high-rotation-speed application conditions.SUMMARY

[0004] An object of the present disclosure is to solve at least the drawbacks existing in the prior art, proposing a bearing comprising a bearing body and a bearing cap, wherein the bearing body comprises a radially bearing inner race and a radially bearing outer race, one of the bearing inner race and the bearing outer race being a rotating race and the other being a stationary race; the bearing cap has an annular shape and is configured to fit with the bearing body such that a bearing cavity is formed between the bearing cap and the bearing body.

[0005] The bearing cap includes: a first section located on a side of the bearing cap adjacent to the rotating race, the first section being made of metal, the first section being fitted with the rotating race; and a second section located on a side of the bearing cap adjacent to the stationary race, the second section being made of a non-metal, wherein the second section is press-fitted with the stationary race, and a material of which the stationary race is made has a modulus of elasticity greater than 600 times of a modulus of elasticity of the non-metal material of which the second section is made.

[0006] According to some embodiments of the present disclosure, the second section is made of an elastomeric material, the material from which the stationary race is made has an elastic modulus of 200 Gpa or more, and the elastomeric material has an elastic modulus of 300 Mpa or less.

[0007] According to some embodiments of the present disclosure, the bearing satisfies Do< di + A * di '9, wherein Dois the outer diameter of the bearing outer race, dtis an inner diameter of the bearing inner race, and A is a proportionality factor and is 0.62 or less.

[0008] According to some embodiments of the present disclosure, the stationary race is the bearing outer race, the bearing outer race including a blocking portion having a minimum diameter that is less than a maximum diameter of the second segment, the second segment located axially inward of the blocking portion; or the stationary race is the bearing inner race, the bearing inner race including a blocking portion having a maximum diameter that is greater than a minimum diameter of the second segment, the second segment located axially inward of the blocking portion.

[0009] According to some embodiments of the present disclosure, the stationary race is the bearing outer race, a maximum diameter of the first section being less than a minimum diameter of the blocking portion of the bearing outer race; or the stationary race is the bearing inner race, the minimum diameter of the first section being larger than the maximum diameter of the blocking portion of the bearing inner race.

[0010] According to some embodiments of the present disclosure, the stationary race is the bearing outer race having a receptacle which is adjacent to the blocking portion and is a groove opening radially inward, the second segment being press fit with the bearing outer race at the receptacle; or the stationary race is the bearing inner race having areceptacle which is adjacent to the blocking portion and is a groove opening radially outward, the second section being press fit with the bearing outer race at the receptacle.

[0011] According to some embodiments of the present disclosure, the first section of the bearing cap is in clearance fit with the rotating race of the bearing body.

[0012] According to some embodiments of the present disclosure, the first section comprises: a base generally parallel to a radial direction of the bearing body; a first outer bend segment located radially outward of the base and at an obtuse angle to the base; a second outer bent segment located radially outward of the first outer bent segment and substantially parallel to the base. The first outer bent segment and second outer bent segment abut the second section.

[0013] According to some embodiments of the present disclosure, the first outer bent segment bends axially inward from the base, the base and the first outer bent segment having an angle between 120 ° and 140 °.

[0014] According to some embodiments of the present disclosure, the stationary race is the bearing outer race, and the diameter of the intersection of the first outer bent segment and the second outer bent segment is greater than or equal to d0— 0.05£>r, wherein, d0is the inner diameter of the bearing outer race, and Dris the diameter of the rolling element.

[0015] According to some embodiments of the present disclosure, the rotating race is the bearing inner race having an inner diameter of 15 mm or more, and the first section further includes an inner bent end on a radially inner side.

[0016] According to some embodiments of the present disclosure, the inner bent end bends axially inward and is substantially perpendicular to the base.

[0017] According to some embodiments of the present disclosure, the second segment extends radially outward from an intersection of the first outer bent segment of the first segment and the base.

[0018] According to some embodiments of the present disclosure, the second section has a recess with an opening orientation that is not parallel to a radial direction.

[0019] According to some embodiments of the present disclosure, the first section and the second section are secured.

[0020] According to some embodiments of the present disclosure, the first section is formed by stamping and the second section is molded on the first section by a molding process.

[0021] According to some embodiments of the present disclosure, the distance of a point on an axially outer side of the base of the first section from a plane in which a respective second end face lies is between 0.1 mm and 0.2 mm.BRIEF DESCRIPTION OF DRAWINGS

[0022] FIG. 1 shows a cross-sectional schematic view of a structure of a bearing cap according to an embodiment of the present disclosure;FIG. 2 shows a schematic cross-sectional view of the fitting state of the bearing cap of the embodiment shown in Figure 1 and bearing body;FIG. 3 shows a schematic cross-sectional view of a structure of a bearing cap according to another embodiment of the present disclosure;FIG. 4 shows a schematic cross-sectional view of the fitting state of the bearing cap of the embodiment shown in Figure 3 and the bearing body

[0023] REFERENCE NUMERALS1 bearing cap, 11 first section, 110 second outer bent section, 111 first outer bent section, 112 base, 113 inner bent end, 114 first end face, 12 second section, 122 recess2 bearing body, 21 bearing outer race, 211 blocking portion, 212 receptacle, 22 bearing inner race, 23 bearing cavity, 24 second end face, 25 rolling element, 26 rolling element cageDETAILED DESCRIPTION

[0024] In order to make the objectives, solutions and advantages of the technical solutions of the present disclosure more clear, a clear and complete description will be made hereinafter of the technical solutions of the embodiments of the present disclosurein conjunction with the accompanying drawings of the specific embodiments of the present disclosure. Terms used herein have their ordinary meaning in the art unless otherwise specified. Like numbers refer to like parts in the drawings.

[0025] Throughout the description of the present application, it should be noted that, unless expressly specified and limited otherwise, the terms "mounted", "connected", "connected", and "connected" are to be understood broadly, e.g., fixedly connected, detachably connected, or integrally connected; Mechanical or electrical connections; The connection may be direct or indirect through an intermediate medium, and may be internal to the two elements. The specific meaning of the above terms in the present application can be understood by those of ordinary skill in the art on a specific occasion. Furthermore, "inner diameter" and "outer diameter" are to be understood in this technical field as well as in the present application as the inner circular diameter and the outer circular diameter of a component.

[0026] In the present application, all shown are schematic cross-sectional views, so that the figure does not directly show the annular shape. However, it is conceivable that one side portion of a cross-section of the corresponding bearing taken on a plane passing through the central axis of the bearing is shown as the corresponding schematic view.

[0027] For ease of description, in the present application, since both the bearing body and the bearing cap are annular components, radial is designated as the direction in which the radius of the bearing body and the bearing cap of the annular shape lies, wherein radially inward is designated as pointing toward the center of the annular shape, as opposed to the direction indicated by the arrow R in FIG. 1, and radially outward is designated as facing away from the center of the annular shape, as indicated by the arrow R in FIG. 1. Further, both axially inward and axially outward refer to directions that are perpendicular to the radial direction, axially outward refers to a direction from the inside of the bearing towards the outside of the bearing, and axially inward refers to a direction from the outside of the bearing towards the inside of the bearing. And it is conceivable that, since both the bearing cap 1 and the bearing body 2 are substantially bodies of revolution, at any point in the bearing cap 1 and the bearing body 2, a circle passing through the point can be taken on the bearing cap 1 and the bearing body 2 with a plane perpendicular to the axis of revolution, the larger the diameter of the circle passing through the point, i.e.,the larger the distance of the point from the axis of revolution, the further out the point in the radially outward direction( i.e., the further to the right in Figs. 2 and 4).

[0028] In this disclosure, substantially parallel refers to relative angles within 180 ° ± 10 °, and substantially perpendicular refers to relative angles within 90 ° ± 5 °.

[0029] When the full metal bearing cap is assembled with the corresponding bearing body, the contact abutment of the bearing outer race with the bearing cap is an accommodation recess to accommodate the maximum diameter of the bearing cap, and the diameters of both sides of the accommodation recess in the axial direction are smaller than the maximum diameter of the bearing cap. In general, such an all-metal bearing cap is relatively stiff and mounting of the bearing cap in the bearing body is caused by pressing. Since the diameter of the axially outward side of the accommodation recess is smaller than the maximum diameter of the bearing cap, it is liable to cause deformation of the bearing outer race when press-fitting the bearing cap. And when the bearing cap is pressed into the accommodation recess, deformation occurs and a pressure is generated on the bearing outer race in the radially outward direction, which will further cause deformation of the bearing outer race. In particular for thin-walled type bearings, these may cause the bearing to be completely scrapped.

[0030] In accordance with embodiments of the present disclosure, improvements are made on the basis of an all-metal bearing cap that can reduce the likelihood of the above- mentioned problems occurring.

[0031] As shown in the embodiment of Fig. 1, the bearing cap 1 may comprise a first section 11 and a second section 12, wherein the first section may be made of a relatively stiff material, such as metal, to ensure the overall strength and stability of the bearing cap 1 and to make the bearing cap 1 suitable for use in high temperature and high rotational speed use scenarios. The first section 11 may include a base 112, a first outer bent section 111, and a second outer bent section 110. In the assembled state, the base 112 is a straight section substantially parallel to the radially outward direction R, the second outer bent section 110 is a radially outer end of the first section 11, the first outer bent section 111 is located between the second outer bent section 110 and the base 112. The first outer bent section 111 and the second outer bent section 110 abut the second section 12. The first outer bent section 111 extends bent at an angle from the base 112. Such bent structuresignificantly strengthens the bearing cap 1 and improves the resistance of the bearing cap 1 to deformation, as compared to a straight, unbent structure.

[0032] Fig. 2 shows a schematic cross-sectional view of the fitting state of the bearing cap 1 of Fig. 1 and a bearing body 2, wherein it can be seen that the bearing cap 1 is fitted between an bearing inner race 22 and an bearing outer race 21 of the bearing body 2. The bearing outer race 21 may be a stationary race and the bearing inner race 22 may be a rotating race which rotates relative to the stationary race. The two symmetrical bearing caps 1 are fitting with the bearing body 2 to form a bearing cavity 23 within which the rolling element 25 as well as the rolling element cage 26 are mounted.

[0033] The bearing cap 1 according to some embodiments of the present disclosure is adaptable to a thin-walled bearing, in particular, to the bearing body 2 satisfying Do< d, + Ad9'9, wherein Dois the outer diameter of the bearing outer race 21, d, is the inner diameter of the bearing inner race 22, and A is a proportionality factor and is 0.62 or less. The bearing outer race 21 of this type of bearing is more susceptible to deformation and is therefore more suitable for the bearing cap 1 according to the above-described embodiments of the present disclosure.

[0034] In some embodiments, the first outer bent segment 111 may bend axially inward from the base 112, and the angle at which the first outer bent segment 111 meets the base 112 may be obtuse, such as between 120 ° and 140 °. As shown, the second outer bent segment 110 of the first section 11 is substantially parallel to the base 112 and can be supported on the bearing outer race 21 through the second section 12 in a direction substantially perpendicular to the radially outward direction R. Such bent structure enables the base 112 to be further outword in the axial direction, increases the volume of the bearing cavity 23, reduces the possibility of interference of the bearing cap with the rolling element 25 and rolling element cage 26 within the bearing cavity 23, and advantageously increases the variety of arrangements and structures within the bearing cavity 23.

[0035] In some embodiments, the diameter of the intersection of the first and second outer bend segments may be greater than or equal to d0- 0.05 Dr, wherein, d0is the inner diameter of the bearing outer race 21, Dris the diameter of the rolling element 25.Thereby, it is ensured that the bearing cap 1 does not interfere with the rolling element 25 and the rolling element cage 26 within the bearing cavity 23.

[0036] As shown in Fig. 2, the first section 11 is clearance fit with the bearing inner race 22, which prevents friction of the bearing cap 1 with the bearing inner race 22. It is advantageous for the rotational performance of the bearing, and thus the bearing can be suitable for use scenarios of high-speed rotation. It should be noted that the clearance may be adjusted according to the particular type, size, and environment of use of the bearing. The bearing cavity 23 is thus an incompletely sealed chamber, which does not affect the rotation of the bearing rotating race due to the clearance fit between the bearing cap 1 and the bearing rotating race , while at the same time allowing a certain amount of lubricant to be present in the bearing cavity 23 without leaking out, and preventing foreign contaminant from entering the bearing cavity 23 to a certain extent.

[0037] In some embodiments, when the bearing cap 1 and the bearing body 2 are in an assembled state, a point on the axially outer side of the base 112 of the bearing cap 1, such as a point on a face 114, is at a distance of between 0.1 mm and 0.2 mm from a plane in which the respective axially outermost second end face 24 of the bearing body lies.

[0038] FIG. 3 shows a schematic cross-sectional view of the structure of a bearing cap according to another embodiment of the present disclosure, where it can be seen that the first section 11 may further comprise an inner bent end 113 located at an end opposite the first outer bent section 111. The inner bent end 113 increases the mating area with the bearing inner race 22, and the sealing performance of the bearing cap 1 can be improved. For example, according to some embodiments, the inner diameter of the bearing inner race 22 is 6 mm or less, and the inner bent end 113 may not be provided due to under sizing; according to other embodiments, the inner diameter of the bearing inner race 22 is between 6 mm and 15 mm and an inner bent end 113 may be provided; according to further embodiments, the inner diameter of the bearing inner race 22 is 15 mm or more, and it’s particularly preferable to provide with the inner bent end 113 to increase the sealing performance.

[0039] As shown in FIG. 4, the inner bent end 113 may be bent axially inward from the base 112, and the inner bent end 113 may be substantially perpendicular to the base 112to improve spatial compactness of the structure and prevent the possibility of inner bent end 113 protruding bearing sides that may result from the inner bent end 113 extending axially outward.

[0040] As shown in Fig. 1 and Fig. 3, the second section 12 is adjacent to the first section 11, i.e. to the first outer bent section 111 and the second outer bent section 110. The second section 12 extends in the radially outward direction R from the intersection of the first outer bent section 111 with the base 112 to achieve a half-enclosure of the first outer bent section 111 and a full enclosure of the second outer bent section 110, so that the structure and characteristics of the radially outer segment of the bearing cap 1 adjacent to the bearing outer race 21 can be significantly changed with less influence on the radially inside of the bearing cap 1. The stiffness of the second section 12 is much less than that of the bearing outer race 21, for example, the modulus of elasticity of the material from which the second section 12 is made may be much less than the modulus of elasticity of the material from which the bearing outer race 21 is made. Specifically, the modulus of elasticity of the material from which the bearing outer race 21 is made is greater than 600 times the modulus of elasticity of the non-elastic material from which the second section 12 is made. For example, the second section 12 is made of an elastomeric material, such as a rubber material, an ethylene-based elastomer, a propylene-based elastomer, a polyester elastomer, or the like. While the elastic modulus of the material from which the bearing outer race 21 is made may be 200 Gpa or more, the elastic modulus of the selected elastomeric material may be 300 Mpa or less. The huge difference of the elastic moduli enables the second section 12 of the bearing cap 1 to be significantly deformed to guarantee the sealing performance when the bearing cap 1 is press-fitted with the bearing outer race 21, while the bearing outer race 21 is almost non-deformed, the roundness of the bearing outer race 21 is guaranteed, and the use stability of the bearing is improved.

[0041] In some embodiments, the second section 12 may also include a recess 122 having an opening direction that is non-parallel to the radially outward direction R, such as the opening direction may be substantially perpendicular to the radially outward direction R, as shown in FIGS. 1 and 3. The provision of the recess 122 further reduces the stiffness of the second section 12 in the radially outward direction R, leaving space for the deformation of the second section 12, so that the second section 12 more easilytends to deform when press-fitted, further reducing the radial force on the bearing outer race 21. As shown in Figures 2 and 4, this recess 122 may be provided on an axially outward side of the second section 12 to correspond to the shape of the first outer bent section 111 of the first section 11.

[0042] The first section 11 and the second section 12 may be secured together to form a one-piece component to increase the sealing performance and stability of the bearing cap 1. For example, the first section 11 may be stamped and then the second section 12 may be molded onto the first section 11 to simplify the manufacturing process of the bearing cap 1.

[0043] As shown in Fig. 2 and Fig. 4, the bearing outer race 21 comprises blocking portion 211 which may be provided at the two second end faces 24 axially outside the bearing outer race 21. The blocking portions 211 may abut against at least a portion of the bearing cap 1, limiting the bearing cap 1 and reducing the possibility of unintentional disengagement caused by axially outward relative movement of the bearing cap 1.

[0044] In some embodiments, the bearing outer race 21 may further comprise a receptacle 212, which is a groove having an opening direction opposite to the radially outward direction R and may be adjacent to the blocking portion 211. The receptacle 212 is used for receiving a portion of the second section 12 of the bearing cap 1, increasing the mating area of the bearing cap 1 with the bearing outer race 21, greatly increasing the sealing performance of the bearing cap. A side of the receptacle 212 proximate the bearing cavity 23 may abut at least a portion of the bearing cap 1, limiting the bearing cap 1 and reducing the possibility of interference of the bearing cap 1 with components within the bearing cavity 23 caused by axial inward relative movement of the bearing cap 1.

[0045] A person skilled in the art can conceive that the design of the bearing cap of some embodiments of the present disclosure may have an opposite structure, i.e. the bearing inner race being a stationary race and the bearing outer race being a rotating race. Therefore, the above-described design of the bearing cap will also have a corresponding adaptation, interchanging the first section with the second section upside down, i.e. the first section on the radial outside mates with the bearing outer race and the second sectionon the radial inside mates with the bearing inner race, the other structures and cooperation being adapted accordingly with reference to the previous embodiments.

[0046] It is to be understood that the above description is intended to be illustrative, and not restrictive. For example, the above-described embodiments (and / or aspects thereof) may be used in combination with each other. In addition, many modifications may be made to adapt a particular situation or material to the teachings of the present disclosure without departing from its scope. The functions or performances of the various elements or modules described herein are for illustration only and are in no way limiting, but are merely exemplary embodiments. Many other embodiments and modifications within the spirit and scope of the claims will be apparent to those of skill in the art upon reviewing the above description. The scope of the disclosure should, therefore, be determined with reference to the appended claims, along with the full scope of equivalents to which such claims are entitled.

[0047] In the appended claims, the terms "including" and "in which" are used as the plain-English equivalents of the respective terms "comprising" and "wherein." Moreover, in the following claims, the terms "first," "second," and "third," etc. are used merely as labels, and are not intended to impose numerical requirements on their objects.

Claims

CLAIMS1. A bearing comprising a bearing body and a bearing cap, the bearing body including a bearing inner race located on a radially inner side and a bearing outer race located on a radially outer side, one of the bearing inner race and the bearing outer race being a rotating race and the other being a stationary race; the bearing cap having an annular shape and configured to fit with the bearing body such that a bearing cavity is formed therebetween, the bearing cap comprising: a first section located on a side of the bearing cap adjacent to the rotating race, the first section being made of metal, the first section fitting with the rotating race; and a second section located on a side of the bearing cap adjacent to the stationary race, the second section being made of a non-metal material, wherein the second section is press-fit with the stationary race, and a material from which the stationary race is made has a modulus of elasticity greater than 600 times that of the non-metal material from which the second section is made.

2. The bearing according to claim 1 , wherein, the second section is made of an elastomeric material, the material from which the stationary race is made has an elastic modulus of 200 Gpa or more, and the elastomeric material has an elastic modulus of 300 Mpa or less.

3. The bearing according to claim 1 satisfiesDo< di + A * d9 9wherein, Dois the outer diameter of the bearing outer race, di is an inner diameter of the bearing inner race, and A is a proportionality factor and is 0.62 or less.

4. The bearing according to claim 1 , wherein, the stationary race is the bearing outer race, the bearing outer race including a blocking portion having a minimum diameter that is less than a maximum diameter of the second segment, the second segment located axially inward of the blocking portion; orthe stationary race is the bearing inner race, the bearing inner race including a blocking portion having a maximum diameter that is greater than a minimum diameter of the second segment, the second segment located axially inward of the blocking portion.

5. The bearing according to claim 4, wherein, the stationary race is the bearing outer race, a maximum diameter of the first section being less than a minimum diameter of the blocking portion of the bearing outer race; or the stationary race is the bearing inner race, the minimum diameter of the first section being larger than the maximum diameter of the blocking portion of the bearing inner race.

6. The bearing according to claim 4, wherein, the stationary race is the bearing outer race having a receptacle which is adjacent to the blocking portion and is a groove opening radially inward, the second segment being press fit with the bearing outer race at the receptacle; or the stationary race is the bearing inner race having a receptacle which is adjacent to the blocking portion and is a groove opening radially outward, the second section being press fit with the bearing outer race at the receptacle.

7. The bearing according to claim 1 , wherein, the first section of the bearing cap is in clearance fit with the rotating race of the bearing body.

8. The bearing according to claim 7, wherein the first section comprises: a base generally parallel to a radial direction of the bearing body; a first outer bend segment located radially outward of the base and at an obtuse angle to the base; a second outer bent segment located radially outward of the first outer bent segment and substantially parallel to the base, wherein the first outer bent segment and second outer bent segment abut the second section.

9. The bearing according to claim 8, wherein, the first outer bent segment bends axially inward from the base, the base and the first outer bent segment having an angle between 120 ° and 140 °.

10. The bearing according to claim 8, wherein, the stationary race is the bearing outer race, and the diameter of the intersection of the first outer bent segment and the second outer bent segment is greater than or equal to d0- 0.05Drwherein, d0is the inner diameter of the bearing outer race, Dris the diameter of the rolling element.

11. The bearing according to claim 8, wherein, the rotating race is the bearing inner race ing an inner diameter of 15 mm or more, and the first section further includes an inner bent end on a radially inner side.

12. The bearing according to claim 11, wherein, the inner bent end bends axially inward and is substantially perpendicular to the base.

13. The bearing according to claim 8, wherein, the second segment extends radially outward from an intersection of the first outer bent segment of the first segment and the base.

14. The bearing according to claim 1, wherein, the second section has a recess with an opening orientation that is not parallel to a radial direction.

15. The bearing according to any one of the preceding claims, wherein the first section and the second section are secured.

16. The bearing according to claim 15, wherein,the first section is formed by stamping and the second section is molded on the first section by a molding process.

17. The bearing according to claim 1, wherein, the distance of a point on an axially outer side of the base of the first section from a plane in which a respective second end face lies is between 0.1 mm and 0.2 mm.

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