A new type of bearing cage

Abstract

The present invention provides a novel bearing cage. The cage is a cylindrical structure composed of a left ring, a right ring, and multiple cross beams connected between the two rings. Pocket holes for placing rolling elements are provided between adjacent cross beams. Fluid grooves are symmetrically arranged at positions corresponding to the cross beams on the two side rings of the cage. The fluid grooves are evenly distributed along the circumferential direction of the two side rings on the inner ring surface or the outer ring surface of the side rings, and the opening area of the fluid grooves is larger than the bottom area. When the cage is externally guided, the fluid grooves are axially penetrating outer ring concave portions formed on the outer guiding surface of the cage side ring; when the cage is internally guided, the fluid grooves are axially penetrating inner ring concave portions formed on the inner guiding surface of the cage side ring. By utilizing the hydrodynamic pressure characteristics, when the bearing rotates at high speed, the present invention can make the cage float on the rotation axis of the bearing, reduce the vibration and noise of the bearing, improve the rotation accuracy, and extend the service life of the bearing.

Description

Technical Field

[0001] The present invention relates to the field of bearings, and specifically to a novel bearing cage. Background Art

[0002] A bearing cage is used in a bearing to evenly isolate rolling elements, maintain the correct attitude and position of the rolling elements during operation, and keep the rolling elements from falling out of the bearing. It is an important component to ensure the normal operation of the bearing. When the bearing is working, the cage needs to be guided to ensure the concentric rotation of the cage. The guiding methods of the cage are generally divided into three types: 1. Outer-ring guiding (abbreviated as outer guiding). The characteristic of this structure is that the clearance between the outer diameter of the cage and the inner diameter of the outer ring is very small. The cage is radially positioned by the outer ring. These two circumferential surfaces with very small clearances are collectively called guiding surfaces. 2. Inner-ring guiding (abbreviated as inner guiding). The characteristic of this structure is that the clearance between the inner diameter of the cage and the outer diameter of the inner ring is very small. The cage is radially positioned by the inner ring. These two circumferential surfaces with very small clearances are also collectively called guiding surfaces. 3. Rolling-element guiding. The characteristic of this structure is that the radial clearances between the inner and outer diameters of the cage and the inner and outer rings of the bearing are very large. The cage is radially positioned by the rolling elements. In addition, through the combination of the above three guiding methods, a variety of composite guiding methods can be derived.

[0003] For the above-mentioned outer guiding and inner guiding methods, the cage is radially positioned by the outer or inner ring of the bearing, which is collectively called ring guiding. For a bearing using ring guiding, since there is a certain clearance between the two guiding surfaces, the axis of the cage is offset from the rotation axis of the bearing. When the bearing rotates at high speed, the cage will vibrate violently around the rotation axis of the bearing, seriously affecting the rotation accuracy of the bearing and generating high-frequency noise, and also affecting the service life of the bearing.

[0004] The application publication number CN109996970A discloses a cage and a rolling bearing equipped with the cage. The cage disclosed in this patent is provided with a guiding surface, an avoidance surface, and an axial groove. The axial groove extends from the pocket hole on the outer diameter surface of the cage to the axial end, axially cutting the guiding surface of the cage and forming an axial step portion. A cylindrical roller bearing integral cage disclosed in the authorized publication number CN201606409U has a number of arc-shaped grooves evenly formed on the outer ring surface of the side ring. Although the above two disclosed patents have grooves formed on the guiding surface, the positions of the above grooves are all corresponding to the positions of the pocket holes. Moreover, the main function of the groove (axial groove) provided in the patent of application publication number CN109996970A is to quickly discharge the grease, which can avoid the grease adhering to the rolling elements, reduce the heat generated due to the stirring resistance of the grease, and inhibit the decline of the service life of the rolling bearing; the groove provided in the patent of authorized publication number CN201606409U is only for improving the lubrication condition of the guiding surface and reducing the temperature rise of the bearing. The above cages cannot achieve the suspension of the cage on the rotation axis of the bearing, and have a poor effect on reducing the friction between the guiding surface of the cage and the guiding surface of the outer ring or the inner ring, and cannot reduce the bearing vibration and noise, nor improve the running accuracy and running quality of the bearing. Summary of the Invention

[0005] In order to overcome the above defects, the present invention provides a new type of bearing cage, which can make full use of the hydrodynamic pressure characteristics to ensure that the cage can be suspended on the rotation axis of the bearing when the bearing rotates at high speed. It can not only reduce the vibration and noise of the bearing, but also improve the rotation accuracy of the bearing, thereby extending the service life of the bearing.

[0006] To achieve the above object, the present invention adopts the following technical solution for a new type of bearing cage. The cage is a cylindrical structure composed of a left side ring, a right side ring, and a plurality of cross beams connected between the two side rings. Pocket holes for placing rolling elements are provided between adjacent cross beams. The characteristics are as follows: Fluid grooves are symmetrically arranged at the positions corresponding to the cross beams on the left side ring and the right side ring of the cage. At least four fluid grooves are provided on each side ring. The fluid grooves are grooves with a large opening and a small bottom formed on the inner ring surface or the outer ring surface of the side ring of the cage, or straight cutting surfaces directly formed on the outer ring surface of the side ring of the cage, and a plurality of fluid grooves are evenly distributed along the circumferential direction of the left side ring and the right side ring; when the cage is an outer-guided cage, the guiding surface of the cage is arranged on the outer ring surfaces of the left side ring and the right side ring, and the fluid groove is an axially penetrating outer ring concave portion formed on the outer guiding surface of the side ring of the cage; when the cage is an inner-guided cage, the guiding surface of the cage is arranged on the inner ring surfaces of the left side ring and the right side ring, and the fluid groove is an axially penetrating inner ring concave portion formed on the inner guiding surface of the side ring of the cage.

[0007] Further technical solution of the present invention: When the cage is used for a bearing with cylindrical rolling elements, the corresponding pocket is a square pocket, and annularly distributed oil storage grooves are symmetrically arranged on the inner side faces of the left ring and the right ring opposite to each other; the annular oil storage grooves are opened on one side of the cage side ring close to the outer guiding surface or the inner guiding surface, and after the rolling elements are installed on the cage, an annular gap space is formed between the two ends of the rolling elements and the cage.

[0008] Preferred technical solution of the present invention: When the cage is an outer-guided cage, both the left ring and the right ring protrude towards the outer ring surface of the cylindrical structure to form an outer-convex guiding part, and its outer guiding surface is located on the outer ring surface of the outer-convex guiding part; when the cage is an inner-guided cage, the left ring and the right ring protrude towards the inner ring surface of the cylindrical structure to form an inner-convex guiding part, and its inner guiding surface is located on the inner ring surface of the inner-convex guiding part.

[0009] Preferred technical solution of the present invention: Fluid grooves are symmetrically arranged at both ends of each cross beam. When the fluid groove is a groove with a large opening and a small bottom, its radial cross-section is any one of an arc, an isosceles trapezoid, a V shape, a triangle, a semicircle, a fan-shaped ring, an isosceles trapezoid with two curved waists, or a streamline shape with a large opening and a small bottom; when the fluid groove is a straight cutting surface directly formed by cutting the outer ring surface of the cage side ring, the cutting surface forms a concave surface relative to the arc surface of the cage.

[0010] Further technical solution of the present invention: The distance h between the lowest point of the depression of the fluid groove and the guiding surface is less than the distance between the guiding surface and the position at half of the radial thickness of the cross beam; the sum of the opening circumferential lengths L values of all the fluid grooves is 15% - 75% of the circumference of the cage guiding surface.

[0011] Preferred technical solution of the present invention: The included angle a between the tangent line of the concave surface or the side surface of the fluid groove passing through point P and the tangent line of the guiding surface passing through point P is 5° - 75°, and the point P is the intersection point of the concave surface or the side surface of the fluid groove and the guiding surface.

[0012] Preferred technical solution of the present invention: The oil storage groove is a groove body structure with a right triangle, a square, or a right trapezoid axial cross-section formed by vertically cutting or obliquely cutting from the outer guiding surface of the cage towards the center of the cage or from the inner guiding surface of the cage towards the outer ring on the left ring and the right ring of the cage.

[0013] Further technical solution of the present invention: The length of the groove opening width b of the oil storage groove is less than or equal to 3 / 4 of the thickness of the side ring, and the depth c of the oil storage groove body is less than or equal to the distance between the position at half of the radial thickness of the cross beam and the guiding surface.

[0014] Taking external guidance as an example, the principle of the present invention is described. When the cage of the present invention is an externally-guided cage, the fluid grooves can establish a wedge-shaped fluid channel with a large inlet and a small outlet between the two guiding surfaces. The X surface is the surface where the fluid groove intersects with the cage guiding surface. When the cage rotates, the X surface will be subjected to the force F of the fluid (such as grease), and the force F can be decomposed into a force F1 perpendicular to the X surface and a force F2 parallel to the X surface. The forces F1 generated by all the fluid grooves on the circumference of the cage are aggregated, and a resultant force of equal magnitude and all pointing to the rotation axis of the bearing will be formed. At the same time, because the wedge-shaped fluid channel has a large inlet and a small outlet, a large amount of fluid will be squeezed after passing through the outlet and entering between the two guiding surfaces, generating a uniformly distributed force G on the circumference and pointing to the axis. The combined action of the F1 force and the G force makes the cage suspended and rotate stably around the rotation axis of the bearing, greatly improving the operating performance of the bearing. In the bearing with internal guidance, the hydrodynamic pressure generated by this device is uniformly distributed on the circumference of the cage and opposite to the rotation axis of the bearing, and it can also make the cage suspended around the rotation axis of the bearing, achieving the same effect as external guidance.

[0015] Advantages of the present invention:

[0016] (1) In the present invention, a number of axially penetrating fluid grooves are arranged along the circumferential direction on the cage guiding surface, and the opening positions of the fluid grooves are staggered from the positions of the pocket holes. The setting of these fluid grooves can make full use of the hydrodynamic pressure characteristics, ensure that the cage is suspended around the rotation axis of the bearing when the bearing rotates at high speed, not only reduce the vibration and noise of the bearing, but also improve the rotation accuracy of the bearing, thereby extending the service life of the bearing.

[0017] (2) When the present invention is applied to cylindrical bearings, two annular oil storage spaces are provided on the two inner side surfaces corresponding to the two side rings of the cage. The oil storage space forms a gap between the two end surfaces of the cylindrical rolling elements and the cage, which can reduce the friction area between the cage and the rolling elements and increase the oil storage space, which is extremely beneficial to the high-speed rotation of the bearing.

[0018] (3) When the cage rotates, part of the force generated by the fluid on the fluid grooves in the present invention will be decomposed into the centripetal force or centrifugal force on the cage. At the same time, a wedge-shaped fluid channel with a large inlet and a small outlet is established between the two guiding surfaces, which can allow more grease to enter the guiding surface. The greater the oil inlet volume, the greater the extrusion force generated, making the cage suspended and rotate stably around the rotation axis of the bearing, greatly improving the operating performance of the bearing.

[0019] (4) The cage in the present invention is not restricted by the type of lubricating medium. Even when water is used as the lubricant, it can still achieve the effect of suspending the cage around the rotation axis of the bearing, reducing vibration and noise, and improving rotation accuracy.

[0020] (5) In the present invention, the fluid groove is provided at both ends of the cross beam of the cage. There is a cavity jointly formed by the bearing ring, two rolling elements and a cross beam at this position. When the bearing is working, the rolling elements will have two postures of revolution and rotation. Under the action of centrifugal force, each cavity will be filled with fluid (such as grease). Setting the fluid groove at this position will have sufficient fluid participating in the work, providing the necessary working conditions for the fluid groove, so as to fully exert the hydrodynamic pressure characteristics.

[0021] Description of the accompanying drawings

[0022] Figure 1 is a schematic structural diagram of the outer-guided cage in the present invention;

[0023] Figure 2 is a schematic structural diagram of the inner-guided cage in the present invention;

[0024] Figure 3 is an analysis diagram of the force on the outer-guided cage in the present invention;

[0025] Figure 4 is an installation schematic diagram of the present invention as an outer-guided cage;

[0026] Figure 5 is a radial sectional view of the outer-guided cage in the first embodiment of the present invention;

[0027] Figures 6-1 to 6-3 For three different-shaped oil storage grooves in Figure 5 the sectional view in the A - O - A direction;

[0028] Figure 7 is a radial sectional view of the inner-guided cage in the second embodiment of the present invention;

[0029] Figures 8-1 to 8-3 For three different-shaped oil storage grooves in Figure 7 the sectional view in the A - O - A direction;

[0030] Figures 9 to 13 is a radial sectional view of the outer-guided cage with different-shaped fluid grooves;

[0031] Figures 14 to 17 is a radial sectional view of the inner-guided cage with different-shaped fluid grooves;

[0032] In the figure: 1 - left ring, 2 - right ring, 3 - cross beam, 4 - pocket hole, 5 - fluid groove, 5-1 - tangent line of the concave surface of the fluid groove or the groove side surface passing through point P, 5-2 - tangent line of the guiding surface passing through point P, 6 - outer guiding surface, 7 - inner guiding surface, 8 - oil storage groove, 9 - rolling element, 10 - cavity, 11 - inner ring, 12 - outer ring, 13 - outer ring guiding surface, 14 - wedge-shaped fluid channel, P - intersection point of the concave surface of the fluid groove or the groove side surface and the guiding surface. Detailed implementation mode

[0033] The present invention will be further described below in conjunction with the accompanying drawings and embodiments. The attached Figures 1 to 5 All are the drawings of the embodiments, which are drawn in a simplified manner and are only used to clearly and concisely illustrate the purpose of the embodiments of the present invention. The following technical solutions shown in the drawings are the specific solutions of the embodiments of the present invention and are not intended to limit the scope of the present invention to be protected. Based on the embodiments of the present invention, all other embodiments obtained by those of ordinary skill in the art without creative work belong to the scope of protection of the present invention.

[0034] In the description of the present invention, it should be understood that the orientation or positional relationship indicated by the terms "upper", "lower", "inner", "outer", "left", "right", etc. is based on the orientation or positional relationship shown in the drawings, or the orientation or positional relationship in which the product of the invention is usually placed during use, or the orientation or positional relationship commonly understood by those skilled in the art. It is only for the convenience of describing the present invention and simplifying the description, and does not indicate or imply that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore cannot be understood as a limitation to the present invention.

[0035] Embodiment 1 provides an outer-guided bearing cage, which is used for a bearing with cylindrical rolling elements. The specific structure is as Figure 1 and Figure 5 shown. The cage is a cylindrical structure composed of a left ring 1, a right ring 2 and multiple cross beams 3 connected between the two rings. A square pocket hole 4 for placing the rolling elements is provided between adjacent cross beams 3. Both the left ring 1 and the right ring 2 protrude towards the outer ring surface of the cylindrical structure to form an outwardly convex guiding part. An outer guiding surface 6 is formed on the outer ring surface of the outwardly convex guiding part. Fluid grooves 5 are symmetrically arranged at the positions of the left ring 1 and the right ring 2 of the cage corresponding to each cross beam 3. The fluid grooves 5 are axially penetrating outer ring concave parts formed on the outer guiding surface 6 of the side ring of the cage, are evenly distributed along the circumferential direction of the left ring 1 and the right ring 2 on the outer ring surface of the side ring, and the opening area of the fluid grooves 5 is larger than the bottom area. Annularly distributed oil storage grooves 8 are symmetrically provided on the opposite inner side surfaces of the left ring 1 and the right ring 2. As Figures 6-1 to 6-3As shown, the annular oil storage groove 8 is formed on one side of the cage side ring close to the outer guiding surface 6, and after the rolling elements are installed on the cage, an annular gap space is formed and distributed between the two ends of the rolling elements and the cage.

[0036] In the first embodiment, the radial cross-section of the fluid groove 5 can be set as an isosceles trapezoid (as Figure 5 shown), an isosceles trapezoid with convex curved surfaces on both waists (as Figure 9 shown), an isosceles trapezoid with concave curved surfaces on both waists (as Figure 10 shown), an arc (as Figure 11 shown), a V shape (as Figure 12 shown), a straight cutting surface directly formed by cutting the outer ring surface of the cage side ring (as Figure 13 shown). The oil storage groove 8 described in the first embodiment is formed by vertically cutting or obliquely cutting on the left side ring 1 and the right side ring 2 of the cage from the outer guiding surface of the cage towards the center position of the cage, and the axial cross-section is a right triangle (as Figure 6-1 ) or a square (as Figure 6-2 ) or a right trapezoid (as Figure 6-3 ) of the groove body structure.

[0037] The second embodiment provides an inner guiding bearing cage, which is used for a bearing with cylindrical rolling elements. The specific structure is as Figure 2 and Figure 7 shown. The cage is a cylindrical structure composed of a left side ring 1, a right side ring 2 and multiple cross beams 3 connected between the two side rings. Square pocket holes 4 for placing rolling elements are provided between adjacent cross beams 3. The left side ring 1 and the right side ring 2 protrude towards the inner ring surface of the cylindrical structure to form an inner convex guiding part, and an inner guiding surface 7 is formed on the inner ring surface of the inner convex guiding part. Fluid grooves 5 are symmetrically arranged at the positions corresponding to each cross beam 3 on the left side ring 1 and the right side ring 2 of the cage. The fluid grooves 5 are axially penetrating inner ring outer concave parts formed on the inner guiding surface 7 of the cage side ring, and are evenly distributed along the circumferential direction of the left side ring 1 and the right side ring 2 on the inner ring surface of the side ring, and the opening area of the fluid grooves 5 is larger than the bottom area. Annularly distributed oil storage grooves 8 are symmetrically provided on the opposite inner side surfaces of the left side ring 1 and the right side ring 2. The annular oil storage groove 8 is formed on one side of the cage side ring close to the inner guiding surface 7, and after the rolling elements are installed on the cage, an annular gap space is formed and distributed between the two ends of the rolling elements and the cage

[0038] In the second embodiment, the radial cross-section of the fluid groove 5 can be set as an isosceles trapezoid (as Figure 7 shown), an isosceles trapezoid with convex curved surfaces on both waists (as Figure 14 shown), an isosceles trapezoid with concave curved surfaces on both waists (as Figure 15 shown), an arc (as Figure 16 shown), a V shape (as Figure 17as shown). In the second embodiment, the oil storage tank 8 is formed by vertically cutting or obliquely cutting from the inner guiding surface of the cage to the outer ring on the left ring 1 and the right ring 2 of the cage, and the axial section is a right triangle (such as Figure 8-1 ) or a square (as shown in Figure 8-2) or a right trapezoid (such as Figure 8-3 ) of the groove structure.

[0039] When the radial section of the fluid groove 5 in the first embodiment and the second embodiment is an isosceles trapezoid, such as Figure 5 and Figure 7 as shown, the surface where the fluid groove 5 intersects with the guiding surface of the cage is a plane, and the tangent plane at the intersection with the guiding surface will form four angles. When using external guiding, in the direction away from the axis of the cage, the angle closer to the guiding surface and away from the fluid groove is called angle a; when using internal guiding, in the direction closer to the axis of the cage, the angle closer to the guiding surface and away from the fluid groove is called angle a. The maximum radial distance between the lowest point of the fluid groove and the guiding surface is h, and the distance between the two points where the fluid groove intersects with the guiding surface is called L.

[0040] When the radial section of the fluid groove 5 in the first embodiment and the second embodiment is an isosceles trapezoid with convex curved surfaces on both waists, such as Figure 9 and Figure 14 as shown, the surface where the fluid groove 5 intersects with the guiding surface of the cage is a convex curved surface. At the intersection point, the two tangent planes of this convex curved surface and the guiding surface of the cage will form four angles. When using external guiding, in the direction away from the axis of the cage, the angle closer to the guiding surface and away from the fluid groove is called angle a; when using internal guiding, in the direction closer to the axis of the cage, the angle closer to the guiding surface and away from the fluid groove is called angle a. The maximum radial distance between the lowest point of the fluid groove and the guiding surface is h, and the distance between the two points where the fluid groove intersects with the guiding surface is called L.

[0041] When the radial section of the fluid groove 5 in the first embodiment and the second embodiment is an isosceles trapezoid with concave curved surfaces on both waists, such as Figure 10 and Figure 15 as shown, the surface where the fluid groove 5 intersects with the guiding surface of the cage is a concave curved surface. At the intersection point, the two tangent planes of this concave curved surface and the guiding surface of the cage will form four angles. When using external guiding, in the direction away from the axis of the cage, the angle closer to the guiding surface and away from the fluid groove is called angle a. When using internal guiding, in the direction closer to the axis of the cage, the angle closer to the guiding surface and away from the fluid groove is called angle a. The maximum radial distance between the lowest point of the fluid groove and the guiding surface is h, and the distance between the two points where the fluid groove intersects with the guiding surface is called L.

[0042] When the radial section of the fluid groove 5 in the first embodiment and the second embodiment is an arc, such as Figure 11 and Figure 16As shown, the fluid groove 5 is a single arc surface. At the intersection point, four angles are formed between this single arc surface and the two tangent planes of the cage guiding surface. When using external guidance, the angle called angle a is the one that is away from the cage axis direction and closer to the guiding surface and away from the fluid groove; when using internal guidance, the angle called angle a is the one that is closer to the cage axis direction, closer to the guiding surface and away from the fluid groove. The maximum radial distance between the lowest point of the fluid groove and the guiding surface is h, and the distance between the two intersection points of the fluid groove and the guiding surface is called L.

[0043] In the first embodiment and the second embodiment, the radial cross-section of the fluid groove 5 is V-shaped, as Figure 12 and Figure 17 shown, the fluid groove 5 is composed of two intersecting planes, and these two planes respectively intersect with the guiding surface. At the intersection point, four angles are formed between the plane and the tangent plane of the cage guiding surface. When using external guidance, the angle called angle a is the one that is away from the cage axis direction and closer to the guiding surface and away from the fluid groove; when using internal guidance, the angle called angle a is the one that is closer to the cage axis direction, closer to the guiding surface and away from the fluid groove; the maximum radial distance between the lowest point of the fluid groove and the guiding surface is h, and the distance between the two intersection points of the fluid groove and the guiding surface is called L.

[0044] When the fluid groove 5 in the first embodiment is a straight cutting surface directly formed on the outer ring surface of the cage side ring, as Figure 13 shown, its cutting surface forms a concave surface relative to the arc surface of the cage. This shape of the fluid groove 5 is only applicable to the externally-guided cage. At this time, the fluid groove 5 is a plane, and this plane intersects with the guiding surface to form the fluid groove 5. At the intersection point, four angles are formed between the plane and the tangent plane of the cage guiding surface. The angle called angle a is the one that is away from the cage axis direction and closer to the guiding surface and away from the fluid groove. The maximum radial distance between the lowest point of the fluid groove and the guiding surface is h, and the distance between the two intersection points of the fluid groove and the guiding surface is called L.

[0045] In the first embodiment and the second embodiment, the distance h between the lowest concave point of the fluid groove 5 and the guiding surface is less than the distance between the guiding surface and the position at half of the radial thickness of the cross beam 3; the sum of the opening circumferential length L values of all the fluid grooves 5 is 15% - 75% of the circumference of the cage guiding surface. As Figure 5 、 Figure 7 、 Figure 9 、 Figure 10 、 Figure 12 、 Figure 14 、 Figure 15 and Figure 17As shown, when the fluid groove 5 is a groove with a V-shaped, isosceles trapezoidal, isosceles trapezoidal with convex surfaces on both waists, or isosceles trapezoidal with concave surfaces on both waists in the radial cross-section, the angle a between the tangent line 5-1 of the groove side of the fluid groove 5 passing through point P and the tangent line 5-1 of the guiding surface passing through point P is 5° to 75°; as Figure 11 , Figure 13 and Figure 16 shown, when the fluid groove 5 is arc-shaped or has a straight cutting surface, the angle a between the tangent line 5-1 of the concave surface of the fluid groove 5 passing through point P and the tangent line 5-2 of the guiding surface passing through point P is 5° to 75°. The point P is the intersection point of the concave surface or the groove side of the fluid groove 5 and the guiding surface.

[0046] The shape characteristics of the oil storage tank 8 in the first embodiment and the second embodiment are specifically as follows. When the axial cross-section of the oil storage tank 8 is a right triangle, as Figure 6-1 and Figure 8-1 shown, it is a right triangle composed of side b and side c, where the length of side b is less than or equal to 3 / 4 of the thickness f of the side ring, and the length of side c is less than or equal to the distance from the 1 / 2 radial thickness position of the cross beam 3 to the guiding surface. When the axial cross-section of the oil storage tank 8 is square, as Figure 6-2 and Figure 8-2 shown, it is a square groove composed of side b and side c, where the length of side b is less than or equal to 3 / 4 of the thickness f of the side ring, and the length of side c is less than or equal to the distance from the 1 / 2 radial thickness position of the cross beam 3 to the guiding surface. When the cross-section of the oil storage tank 8 along the circumferential direction is a right trapezoid, as Figure 6-3 and Figure 8-3 shown, it is a right trapezoid composed of side b, side c, and side d. The length of side b is less than or equal to 3 / 4 of the thickness f of the side ring, the length of side c is less than or equal to the distance from the 1 / 2 radial thickness position of the cross beam 3 to the guiding surface, and the length range of side d is between 0 and the distance of side b.

[0047] The installation and use methods of the cage in the present invention are the same as those of the existing cage. The installation and working principle process will be further described below in combination with the outer-guided cage in the first embodiment. When installing the outer-guided cage in the first embodiment, as Figure 4 shown, after assembling the outer ring 12, the cage, and the rolling elements 9 together, then installing the inner ring 11 of the bearing, the outer guiding surface 13 of the outer ring contacts the outer guiding surface 6 of the cage. Since a cavity 10 is formed between the outer ring 12, the rolling elements 9, and the cross beam 3 of the cage after the cage is installed, during the operation of the bearing, due to the action of centrifugal force, each cavity 10 will be filled with fluid (such as grease). Fluid grooves 5 are respectively provided at the positions of the two side rings of the cage corresponding to the cross beam 3. During rotation, sufficient fluid will enter the fluid grooves from the cavity 10, providing necessary working conditions for the fluid grooves, and thus sufficient fluid dynamic pressure can be generated. When the cage rotates, as Figure 3As shown in the figure, the X surface where the fluid groove 5 intersects with the outer guiding surface 6 of the cage is subjected to the acting force F of the fluid (such as grease). The force F can be decomposed into a force F1 perpendicular to the X surface and a force F2 parallel to the X surface. The forces F1 generated by all the fluid grooves 5 on the circumference of the cage are aggregated, and a resultant force with equal magnitude and all pointing to the rotation axis of the bearing will be formed. The fluid groove is set as a groove with an opening area larger than the bottom area, and a wedge-shaped fluid channel 14 with a large inlet and a small outlet will be formed. After a large amount of fluid passes through the outlet and enters between the two guiding surfaces, it will be squeezed, generating a uniformly distributed acting force G pointing to the axis on the circumference. The combined action of the F1 force and the G force enables the cage to float and rotate stably around the rotation axis of the bearing, greatly improving the operating performance of the bearing.

[0048] On the bearing with inner guidance, the hydrodynamic pressure generated by this device is uniformly distributed on the circumference of the cage and opposite to the rotation axis of the bearing. Similarly, it can make the cage float around the rotation axis of the bearing, achieving the same effect as the outer guidance.

[0049] The above description is only several embodiments of the present invention, and the description is relatively specific and detailed. However, it should not be construed as a limitation to the scope of the present invention. It should be noted that for those of ordinary skill in the art, without departing from the concept of the present invention, several deformations and improvements can still be made, and these all belong to the protection scope of the present invention. Therefore, the protection scope of the present invention should be subject to the appended claims.

Claims

1. A new type of bearing cage, the cage is a cylindrical structure composed of a left ring (1), a right ring (2) and a plurality of cross beams (3) connected between the two rings, and a pocket hole (4) for placing rolling elements is provided between adjacent cross beams (3), and it is characterized in that: Fluid grooves (5) are symmetrically arranged at the positions of the corresponding cross beams (3) of the left ring (1) and the right ring (2) of the cage. At least four fluid grooves (5) are arranged on each side ring. The fluid grooves (5) are grooves with a large opening and a small bottom formed on the outer ring surface of the side ring of the cage. The multiple fluid grooves (5) are evenly distributed along the circumferential direction of the left ring (1) and the right ring (2). The included angle a between the tangent line (5-1) of the concave surface of each fluid groove (5) passing through point P and the tangent line (5-2) of the guiding surface passing through point P is 5° to 75°. The point P is the intersection point of the concave surface of the fluid groove (5) and the guiding surface. The cage is an outer-guided cage, and the guiding surface of the cage is arranged on the outer ring surfaces of the left ring (1) and the right ring (2). The fluid grooves (5) are axially penetrating outer ring concave parts formed on the outer guiding surface (6) of the side ring of the cage. The outer diameters of the left ring (1) and the right ring (2) are larger than the outer diameter of the cylinder composed of multiple cross beams (3). After assembling the cage with the outer ring (12) and the rolling elements (9), the outer ring guiding surface (13) contacts the outer guiding surface (6) of the cage. A cavity (10) is formed between the outer ring (12), the rolling elements (9) and the cage cross beam (3). During the operation of the bearing, due to the action of centrifugal force, each cavity (10) will be filled with fluid. Fluid grooves (5) are respectively arranged at the positions of the corresponding cross beams (3) of the two side rings of the cage. During rotation, sufficient fluid will enter the fluid grooves (5) from the cavity (10).

2. The novel bearing cage according to claim 1, characterized in that: When the cage is used for a bearing with cylindrical rolling elements, the corresponding pocket holes (4) are square pocket holes. Annularly distributed oil storage grooves (8) are symmetrically arranged on the opposite inner side surfaces of the left ring (1) and the right ring (2). The oil storage grooves (8) are arranged on one side of the two side rings of the cage close to the outer guiding surface (6), and after the rolling elements are installed on the cage, an annular gap space is formed between the two ends of the rolling elements and the cage.

3. A novel bearing cage according to claim 1, characterized in that: Fluid grooves (5) are symmetrically arranged at both ends of each cross beam (3). The fluid grooves (5) are any one of an arc shape, an isosceles trapezoid shape, and a V shape with a large opening and a small bottom in the radial cross section.

4. A novel bearing cage according to claim 1, characterized in that: The distance h between the lowest point of the concave part of the fluid groove (5) and the guiding surface is less than the distance between the guiding surface and the cross beam (3) at the position of half of the thickness in the radial direction; The sum of the opening circumferential lengths L values of all the fluid grooves (5) is 15% to 75% of the circumference of the guiding surface of the cage.

5. A novel bearing cage according to claim 2, characterized in that: The oil storage groove (8) is a groove body structure with a right triangle, a square or a right trapezoid axial cross section formed by vertically cutting or obliquely cutting from the outer guiding surface of the cage towards the center position of the cage on the left ring (1) and the right ring (2) of the cage.

6. A novel bearing cage according to claim 2, characterized in that: The length of the groove opening width b of the oil storage groove (8) is less than or equal to 3 / 4 of the thickness of the side ring, and the depth c of the groove body of the oil storage groove (8) is less than or equal to the distance between the position of half of the radial thickness of the cross beam (3) and the guiding surface.

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