Wear-resistant high-speed deep groove ball bearing

Abstract

The utility model discloses a wear-resistant high-speed deep groove ball bearing, and belongs to the technical field of bearings. The device comprises a bearing inner ring; a bearing outer ring; the retainer is positioned between the bearing inner ring and the bearing outer ring; the holder is provided with an elliptical pocket with a vertical section with a notch; the balls are installed in the pockets, the balls are half-wrapped by the pockets, and the size of the balls is smaller than that of the pockets; when the high-speed ball bearing operates, only part of the balls abut against the inner walls of the pockets. The pockets with the oval vertical sections are formed in the retainer, when the high-speed ball bearing operates, only parts of the balls can make contact with the inner walls of the pockets, the contact area of the pockets of the retainer and the balls is small, abrasion between the retainer and the balls can be reduced, the inner diameter of the portion, making contact with the balls, of the retainer is prevented from being reduced, and the service life of the retainer is prolonged. Bearing fatigue damage is reduced, and long-time normal use of the bearing is guaranteed.

Description

Technical Field

[0001] The utility model relates to the technical field of bearings, and particularly relates to a wear-resistant high-speed deep groove ball bearing. Background Art

[0002] The deep groove ball bearing is the most widely used rolling bearing. The basic type of deep groove ball bearing consists of an outer ring, an inner ring, a set of steel balls and a set of cages. Its characteristics are small friction resistance and high rotational speed. It can be used for parts that can bear radial loads or combined loads with both radial and axial actions simultaneously, and can also be used for parts that bear axial loads, such as small power motors, automotive and tractor gearboxes, machine tool gearboxes, general machinery, tools, etc.

[0003] The main load borne by the cage is the centrifugal force. After the cage is affected by the centrifugal force, the following three impacts will be caused:

[0004] 1) The centrifugal force will cause the deformation of the cage;

[0005] 2) The centrifugal force can strengthen the creep of the cage and further accelerate the deformation of the cage;

[0006] 3) The centrifugal force causes internal stress in the cage.

[0007] The existing cages have the following disadvantages:

[0008] (1) The centrifugal force will cause the deformation of the cage.

[0009] When the bearing runs at high speed, the cage will be affected by the centrifugal force and expand and deform in the radial direction. The higher the rotational speed, the greater the centrifugal force and the greater the expansion deformation. Since the geometric shape of the crown cage is asymmetric axially and the material at the ball pocket position of the cage is circular and closed-loop continuous, the external expansion deformation will be smaller. The positions of the strengthening part and the claw part of the cage are similar to the long bow structure, and its material is discontinuous in the circular direction. Therefore, compared with the ball position, the degree of external expansion deformation will be greater. And the farther away from the ball axis position, the greater the expansion deformation, eventually leading to the external distortion deformation of the cage. Seriously, the outer circular surface of the cage can even interfere with the outer ring of the bearing.

[0010] (2) The centrifugal force can strengthen the creep of the cage and further accelerate the deformation of the cage.

[0011] Under the influence of specific temperature and a small constant external force (such as tensile force, pressure, or torsion) on the oil of the polymer material, the deformation of the polymer material gradually increases with time. During the operation of the bearing, the cage is continuously affected by centrifugal force and the impact force of the rolling elements. As the operation time increases, the bracket may undergo a certain degree of irreversible creep. The creep exacerbates the deformation of the cage, thereby increasing the risk of interference between the cage and the outer ring of the bearing.

[0012] (3) The centrifugal force causes internal stress in the cage.

[0013] When the bearing rotates at high speed, due to the action of centrifugal force, the bracket is distorted, the strengthening part and the position of the pocket claws turn outwards, increasing the internal stress at the bottom of the pocket holes of the cage. The higher the rotational speed, the greater the deformation of the cage and the greater the internal stress. The material at the bottom of the pocket holes of the cage is the least, which is the weakest and most easily damaged position.

[0014] (4) Wear between the cage and the balls.

[0015] When the high-speed ball bearing is in operation, the contact area between the cage and the balls is generally large, and friction inevitably occurs at the contact part between the two, causing wear between the cage and the balls; during long-term use, the wear easily causes a reduction in the inner diameter of the cage at the contact part between the two, and in severe cases, metal powder will fall off, which causes fatigue damage to the bearing and affects the use of the bearing.

[0016] Therefore, various influences on the cage should be fully considered in the design. Utility Model Content

[0017] The purpose of the present utility model is to provide a high-efficiency wear-resistant high-speed deep groove ball bearing.

[0018] To solve the above technical problems, the present utility model provides a wear-resistant high-speed deep groove ball bearing, including:

[0019] Inner ring of the bearing;

[0020] Outer ring of the bearing;

[0021] A cage, which is located between the inner ring and the outer ring of the bearing; the cage is provided with pocket holes with an elliptical vertical cross-section with a notch;

[0022] Balls, which are installed in the pocket holes, the pocket holes semi-encase the balls, and the size of the balls is smaller than the size of the pocket holes; when the high-speed ball bearing is in operation, only part of the balls is in contact with the inner wall of the pocket holes.

[0023] Preferably, the distance from the inner wall of the pocket hole to its center gradually increases from the upper and lower ends of the inner wall to the middle.

[0024] Preferably, the intersection of the bottom of the cage and the pocket is a circular chamfer;

[0025] Preferably, arc-shaped grooves are formed on opposite sides of the inner ring and the outer ring of the bearing;

[0026] The balls are located in the arc-shaped grooves of the inner ring and the outer ring of the bearing.

[0027] Preferably, a plurality of weight-reducing grooves are formed in the cage.

[0028] Preferably, the weight-reducing grooves are located directly above the corresponding pockets.

[0029] Preferably, the number of the weight-reducing grooves is the same as the number of the pockets and they correspond to each other one by one.

[0030] Preferably, nine pockets are circumferentially and uniformly formed at the bottom of the cage;

[0031] Nine weight-reducing grooves are circumferentially and uniformly formed at the top of the cage.

[0032] Preferably, the cage is a glass fiber reinforced polyimide cage.

[0033] Preferably, positioning protrusions are provided on the inner walls of the arc-shaped grooves of the inner ring and the outer ring of the bearing;

[0034] The positioning protrusions are used to position the balls.

[0035] Compared with the prior art, the beneficial effects of the present utility model are as follows:

[0036] In the present utility model, pockets with an elliptical cross-section are formed in the cage, and there is a part of a notch at the lower part of the pocket. There is a gap between the balls and the pockets. When the high-speed ball bearing rotates, only part of the balls will contact the inner walls of the pockets. The contact area between the pockets of the cage and the balls is small, which can reduce the wear between the cage and the balls, avoid the reduction of the inner diameter of the cage at the contact part between the two, reduce the fatigue damage of the bearing, and ensure the long-term normal use of the bearing.

[0037] In addition, the pockets of the present utility model semi-encase the balls, avoiding the external distortion and deformation of the cage. The intersection of the bottom of the cage of the high-speed ball bearing of the present utility model and the pocket is a circular chamfer, which is convenient for embedding the balls into the pockets; only one cage is used for the bearing, which can reduce the thickness of the overall structure. Weight-reducing holes are formed at the top of the cage, thereby reducing the weight of the cage and reducing the internal stress generated by the cage; the cage of the present utility model is made of glass fiber reinforced engineering plastic, which has a lighter mass and lower friction performance, reducing the risk of interference between the cage and the outer ring of the bearing. Description of the Drawings

[0038] The following further describes in detail the specific embodiments of the present utility model in conjunction with the accompanying drawings.

[0039] Figure 1 It is a schematic structural view of the high-speed ball bearing of the present utility model;

[0040] Figure 2 It is a schematic structural view of the cage;

[0041] Figure 3 It is a schematic structural view of the connection between the cage and the ball;

[0042] In the figure:

[0043] 1 - inner ring of the bearing; 2 - outer ring of the bearing; 3 - cage; 31 - pocket; 32 - circular chamfer; 33 - weight reduction groove; 4 - ball; 5 - arc groove; 51 - positioning protrusion. Specific embodiments

[0044] Many specific details are set forth in the following description in order to provide a thorough understanding of the present utility model. However, the present utility model can be implemented in many other ways different from those described herein, and those skilled in the art can make similar extensions without departing from the connotation of the present utility model. Therefore, the present utility model is not limited by the specific embodiments disclosed below.

[0045] The terms used in one or more embodiments of this specification are for the purpose of describing specific embodiments only and are not intended to limit one or more embodiments of this specification. The singular forms "a", "the", and "said" used in one or more embodiments of this specification and the appended claims are also intended to include the plural forms unless the context clearly dictates otherwise. It should also be understood that the term "and / or" used in one or more embodiments of this specification refers to and includes any or all possible combinations of one or more of the associated listed items.

[0046] It should be understood that although the terms first, second, etc. may be used in one or more embodiments of this specification to describe various information, such information should not be limited to these terms. These terms are only used to distinguish the same type of information from each other. For example, without departing from the scope of one or more embodiments of this specification, the first may also be referred to as the second, and similarly, the second may also be referred to as the first. Depending on the context, the word "if" as used herein may be interpreted as "when" or "while" or "in response to determining".

[0047] The following further describes the present utility model in detail in conjunction with the accompanying drawings:

[0048] The present utility model provides a wear-resistant high-speed deep groove ball bearing, including:

[0049] Inner ring 1 of the bearing;

[0050] Outer ring 2 of the bearing

[0051] Cage 3, which is located between the inner ring 1 and the outer ring 2 of the bearing; a pocket 31 with an elliptical vertical cross-section having a notch is formed in the cage 3;

[0052] Ball 4, which is installed in the pocket 31, the pocket 31 semi-covers the ball 4, and the size of the ball 4 is smaller than that of the pocket 31; when the high-speed ball bearing rotates, only part of the ball 4 abuts against the inner wall of the pocket 31.

[0053] Preferably, the distance from the inner wall of the pocket 31 to its center gradually increases from the upper and lower ends of the inner wall to the middle.

[0054] Preferably, the intersection of the bottom of the cage 3 and the pocket 31 is a circular chamfer 32;

[0055] Preferably, arc-shaped grooves 5 are formed on the opposite sides of the inner ring 1 and the outer ring 2 of the bearing;

[0056] The ball 4 is located in the arc-shaped grooves 5 of the inner ring 1 and the outer ring 2 of the bearing.

[0057] Preferably, a plurality of weight-reducing grooves 33 are formed in the cage 3.

[0058] Preferably, the weight-reducing grooves 33 are located directly above the corresponding pockets 31.

[0059] Preferably, the number of the weight-reducing grooves 33 is the same as that of the pockets 31 and they correspond one by one.

[0060] Preferably, nine pockets 31 are evenly circumferentially formed at the bottom of the cage 3;

[0061] Nine weight-reducing grooves 33 are evenly circumferentially formed at the top of the cage 3.

[0062] Preferably, the cage 3 is a glass fiber-reinforced polyimide cage.

[0063] Preferably, positioning protrusions 51 are provided on the inner walls of the arc-shaped grooves 5 of both the inner ring 1 and the outer ring 2 of the bearing;

[0064] The positioning protrusions 51 are used to position the ball 4.

[0065] To better illustrate the technical effects of the present invention, the present invention provides the following specific embodiments to illustrate the above technical process:

[0066] Embodiment 1. A wear-resistant high-speed deep groove ball bearing, as Figure 1 、 2 、shown in 3;

[0067] Taking the commonly used 6207 and 6009 bearings in the electric drive system of new energy vehicles as examples, a series of designs for high-speed deep groove ball cage are carried out; the application conditions of high-speed deep groove ball bearings in new energy vehicles require the cage to have the properties of light weight, good self-lubrication and high strength.

[0068] Compared with traditional steel stamping cages, glass fiber-reinforced engineering plastics have lighter mass and lower friction performance, becoming the preferred raw materials to meet the requirements of high rotational speeds. The light cage carrying the rotating elements has less friction than other loading methods during high-speed operation.

[0069] Therefore, when selecting raw materials for high-speed cages from existing conventional materials, glass fiber-reinforced polyimide (PA46-GF) is preferably recommended. However, due to the structural characteristics of deep groove ball bearings, when using this raw material, the product structure is preferably not designed as a window type, but usually an asymmetric crown type is selected for design.

[0070] When the high-speed ball bearing is operating, the main loads on the cage 3 are centrifugal force and the force generated by the rolling elements on it. Starting from the centrifugal force when the entire bearing rotates itself, at a certain rotational speed and during rapid acceleration or deceleration, the influence of the balls 4 on the cage 3 is gradually superimposed. Through comparative analysis one by one, the influence of each condition on the cage 3 is clarified, and corresponding design optimizations for high-speed cages are carried out according to the results.

[0071] In this embodiment, the cage 3 is provided with a pocket 31 whose vertical cross-section is elliptical, and there is a part of notch at the lower part of the pocket 31, so that the pocket 31 semi-covers the balls 4, reducing the contact area between the pocket 31 and the balls 4.

[0072] In this embodiment, the size of the balls 4 is smaller than that of the pocket 31, and there is a certain gap between them. The distance from the inner wall of the pocket 31 to its center gradually increases from the upper and lower ends of the inner wall to the middle; that is, the pocket 31 has a structure that is narrow at both ends and wide in the middle compared with a concentric circle. Since the pocket 31 is elliptical (i.e., the inner walls on both sides of the pocket 31 are arc-shaped) and there is a gap between the balls 4 and the pocket 31, the above structure can ensure that when the high-speed ball bearing is operating, the circular balls 4 will not contact the pocket 31 over a large area. Only part of the balls 4 will abut against the upper half or the lower half of one side of the inner wall of the pocket 31, and only a small arc area of the inner wall of the pocket 31 will contact the balls 4 at the same time. This reduces the contact area between the pocket 31 and the balls 4, and the contact area will also change with the operation of the high-speed ball bearing, which can effectively reduce the wear between the pocket 31 and the balls 4.

[0073] When the high-speed ball bearing is running, the contact area between the pocket 31 of the cage 3 in this embodiment and the ball 4 is small, which can reduce the wear between the cage and the ball, avoid the reduction of the inner diameter of the cage at the contact part of the two, reduce the fatigue damage of the bearing, and ensure the long-term normal use of the bearing.

[0074] In addition, both the inner ring 1 and the outer ring 2 of the bearing are provided with positioning protrusions 51 on the inner wall of the arc groove 5, and the positioning protrusions 51 are used to position the ball 4. When the high-speed ball bearing is running, the ball 4 will generate friction with the positioning protrusions 51 of the inner ring 1 and the outer ring 2 of the bearing, rather than directly contacting the inner wall of the arc groove 5, which can further reduce the roller friction and wear.

[0075] The intersection of the bottom of the cage 3 and the pocket 31 of the high-speed ball bearing in this embodiment is a circular chamfer 32, which is convenient for embedding the ball 4 into the pocket 31. Arc grooves 5 are provided on the opposite sides of the inner ring 1 and the outer ring 2 of the bearing, and the ball 4 is located in the arc grooves 5 of the inner ring 1 and the outer ring 2 of the bearing. The diameter of the vertical section of the pocket 31 gradually increases from the outer diameter surface to the inner diameter surface, which can better fix the ball 4.

[0076] Compared with the existing high-speed ball bearing that uses two cages 3 to fix the balls 4, only one cage 3 is used in this embodiment, which can reduce the overall thickness. A weight reduction groove 33 is provided at the top of the cage 3. The number of weight reduction grooves 33 is the same as and corresponds one by one to the number of pockets 31. The weight reduction groove 33 is located directly above the pocket 31, and the design of the weight reduction groove 33 can reduce the overall weight of the cage 3.

[0077] The data of the high-speed deep groove ball bearing in this embodiment are as follows: PCD diameter is φ53.5 cm; the diameter of the ball 4 is φ11.112 cm; the number of pockets 31 is 9; the product material is PA46-GF30; the designed speed is 2 - 2.5W revolutions.

[0078] The above is only the specific implementation manner of the present invention, but the protection scope of the present invention is not limited thereto. Any changes or substitutions within the technical scope disclosed by the present invention should be covered within the protection scope of the present invention. Therefore, the protection scope of the present invention should be subject to the protection scope of the claims.

Claims

1. A wear-resistant high-speed deep groove ball bearing, characterized in that: Comprising: Inner ring of bearing (1); Outer ring of bearing (2); Cage (3), which is located between the inner ring of bearing (1) and the outer ring of bearing (2); an oval pocket (31) with a notch in its vertical cross-section is formed on the cage (3); Ball (4), which is installed in the pocket (31), the pocket (31) semi - wraps the ball (4), and the size of the ball (4) is smaller than that of the pocket (31); when the high - speed ball bearing rotates, only part of the ball (4) abuts against the inner wall of the pocket (31).

2. The wear - resistant high - speed deep - groove ball bearing according to claim 1, characterized in that: The distance from the inner wall of the pocket (31) to its center gradually increases from the upper and lower ends of the inner wall towards the middle.

3. The wear - resistant high - speed deep - groove ball bearing according to claim 2, characterized in that: The intersection of the bottom of the cage (3) and the pocket (31) is a circular chamfer (32).

4. The wear - resistant high - speed deep - groove ball bearing according to claim 3, characterized in that: Arc grooves (5) are formed on the opposite sides of the inner ring of bearing (1) and the outer ring of bearing (2); The ball (4) is located in the arc grooves (5) of the inner ring of bearing (1) and the outer ring of bearing (2).

5. The wear - resistant high - speed deep - groove ball bearing according to claim 4, characterized in that: A number of weight - reducing grooves (33) are formed on the cage (3).

6. The wear - resistant high - speed deep - groove ball bearing according to claim 5, characterized in that: The weight - reducing grooves (33) are located directly above the corresponding pockets (31).

7. The wear - resistant high - speed deep - groove ball bearing according to claim 6, characterized in that: The number of the weight - reducing grooves (33) is the same as that of the pockets (31) and they correspond one by one.

8. The wear - resistant high - speed deep - groove ball bearing according to claim 7, characterized in that: Nine pockets (31) are circumferentially and evenly formed at the bottom of the cage (3); Nine weight - reducing grooves (33) are circumferentially and evenly formed at the top of the cage (3).

9. The wear - resistant high - speed deep - groove ball bearing according to claim 8, characterized in that: The cage (3) is a glass - fiber - reinforced polyimide cage.

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