High flow hydrodynamic lubricated conical bearing cage

Abstract

The application discloses a high-flow dynamic-lubricated tapered bearing retainer, which comprises a large-end diameter ring, a small-end diameter ring and a plurality of window beams, the window beams are provided with first dynamic flow channels which are opened towards a bearing inner ring surface, the window beams are provided with second dynamic flow channels which are arranged towards a pocket hole surface, the first dynamic flow channels and the second dynamic flow channels are communicated, under the action of centrifugal force and inertial force when the tapered bearing rotates at high speed, lubricating oil in the first dynamic flow channels can enter the second dynamic flow channels and fill the whole second dynamic flow channels, if the rolling element moves towards the window beam direction, the rolling element can contact the lubricating oil in the second dynamic flow channels, the lubricating oil can weaken the impact potential energy of the rolling element as a liquid buffer, meanwhile, the lubricating oil can absorb the friction heat generated between the rolling element and the retainer, the temperature of the retainer is reduced, the retainer is favorably protected to be stable, and the service life of the tapered bearing under the working condition of complex load and high-speed rotation is prolonged.

Description

Technical Field

[0001] This application belongs to the field of bearing cages, and particularly relates to a high-flow dynamic lubrication tapered bearing cage. Background Technology

[0002] Tapered roller bearings have high load-bearing capacity and can withstand combined radial and axial loads. They also have high bearing rigidity. With the trend of lightweighting and miniaturization of automotive transmissions, tapered roller bearings are increasingly used in automotive transmission differentials. The limiting speed of tapered roller bearings is affected by the bearing friction torque. The friction torque of tapered roller bearings is mainly generated by the following reasons: 1) rolling friction TR between the outer ring raceway surface and the roller rolling surface; 2) sliding friction TS between the roller end face and the inner ring flange; 3) sliding friction between the roller and the cage; 4) lubricating oil stirring resistance.

[0003] Therefore, those skilled in the art have conducted extensive research on improving the frictional torque of tapered roller bearings. For example, they have reduced torque (TS) by optimizing the contact position between the roller end face and the flange, and improving the surface roughness of the roller end face and the large flange of the inner ring; reduced torque (TR) by optimizing the internal structural parameters of the bearing (such as contact angle, number of rollers, roller length, roller diameter, etc.); further reduced friction by applying newly developed long-life materials; and focused on reducing lubricating oil stirring resistance by decreasing the distance between the cage and the small flange of the inner ring to reduce the lubricating oil inflow area at the small end, thereby reducing stirring resistance and friction. However, in earlier low-speed applications, the roller and cage... The sliding friction between rollers and the cage is very small, and there is little research and optimization design on the sliding friction between rollers and the cage. However, in the current application conditions of tapered roller bearings, especially under complex loads and high-speed rotation, the cage has to withstand a lot of centrifugal force, impact and vibration. A large amount of sliding friction is generated between the cage and the rolling elements. The rolling elements impact the cage beam and generate a lot of heat. The combined effect of force and heat can lead to cage failure. In severe cases, it can cause cage burns and breakage. The deformation of the cage has a great impact on the stability of the entire bearing. Therefore, the existing technology needs to be further improved and enhanced. Summary of the Invention

[0004] This invention provides a high-flow dynamic lubrication tapered bearing cage to solve the problem that under complex load and high-speed rotation conditions, the high friction and heat generation between the cage beam and rolling elements of the circumferential bearing easily cause the cage to burn and break.

[0005] To achieve the above objectives, the present invention provides the following technical solution:

[0006] A high-flow dynamic lubrication tapered bearing cage includes a large end ring, a small end ring, and multiple window beams. The two ends of each window beam are fixedly connected to the large and small end rings, respectively. The multiple window beams are evenly spaced along the circumference of the cage, and adjacent window beams form window holes for mounting rolling elements. The window beams have a first dynamic flow channel facing the inner ring of the bearing, and a second dynamic flow channel facing the hole. During high-speed rotation of the bearing, lubricating oil can flow from the first dynamic flow channel to the second dynamic flow channel and fill it. When the rolling elements move toward the window beams, they can contact the lubricating oil in the second dynamic flow channel to reduce impact potential energy and reduce frictional heat generation.

[0007] The high-flow dynamic lubrication tapered bearing cage of the present invention has a first dynamic flow channel opened on the cage beam facing the inner ring of the bearing, and a second dynamic flow channel opened on the beam facing the pocket surface. The first and second dynamic flow channels are connected. When the tapered bearing rotates at high speed, under the action of centrifugal force and inertial force, the grease or lubricating oil will move towards the larger end. When the lubricating oil accumulates from the smaller end to the larger end, the lubricating oil usually passes through the beam surface. During the movement along the beam surface, the lubricating oil in the first dynamic flow channel can enter the second dynamic flow channel and fill the entire second dynamic flow channel. When the rolling element moves towards the beam, it can contact the lubricating oil in the second dynamic flow, which acts as a liquid buffer to reduce the impact potential energy of the rolling element. At the same time, it can absorb the frictional heat generated between the rolling element and the cage, reduce the cage temperature rise, and help protect the cage stability and improve the service life of the tapered bearing under complex load and high-speed rotation application conditions.

[0008] In a preferred implementation, the first dynamic flow channel includes a main flow channel arranged along the length of the window beam and a branch flow channel connected to the main flow channel. The branch flow channel is V-shaped, with the large opening of the branch flow channel facing the small end diameter ring. The branch flow channel is connected to the second dynamic flow channel. The lubricating grease enters the branch flow channel as it moves from the small end diameter ring to the large end diameter ring in the first dynamic flow channel, and then enters the second dynamic flow channel from the branch flow channel.

[0009] In a preferred implementation, multiple branch channels are provided at intervals along the length of the main channel, and multiple corresponding second dynamic channels are provided, which are evenly spaced on the window beam facing the pocket.

[0010] In a preferred implementation, the cross-sectional width of the main channel gradually narrows from the small-diameter ring to the large-diameter ring.

[0011] This causes the lubricating oil to experience gradually increasing resistance during movement, thereby reducing the amount of lubricating oil accumulating at the larger end and ensuring that the lubricating oil can be evenly distributed to all parts of the bearing when it is running at high speed.

[0012] In a preferred embodiment, the main flow channel is provided with an oil interception section, which can intercept part of the lubricating oil moving along the main flow channel and allow it to enter the branch flow channel.

[0013] In a preferred embodiment, an oil passage groove is provided at the junction of the window beam and the large end diameter ring and the small end diameter ring. The two ends of the main flow channel are connected to the oil passage groove through branch flow channels. The V-shaped branch flow channel near the large end diameter ring has its large opening facing the large end diameter ring.

[0014] By designing the V-shaped branch flow channel near the large end diameter ring with its large opening facing the large end diameter ring, it is beneficial to guide the lubricating oil into the oil groove, reduce the oil flow resistance, and weaken the impact of the lubricating oil on the window beam under the action of centrifugal and inertial forces during the high-speed operation of the bearing.

[0015] In a preferred implementation, the centerline of the second dynamic flow channel and the centerline of the cage are at an angle θ, satisfying 45°≤θ≤90°.

[0016] In a preferred implementation, the cross-sectional width of the second dynamic flow channel gradually narrows from the inner ring of the bearing to the outer ring of the bearing, and the wide end connects to the branch flow channel.

[0017] The area of ​​the second dynamic flow channel becomes narrower and narrower. The wide end connects to the branch flow channel. When the lubricating oil comes from the branch flow channel to the wide end and enters the narrow space, the lubricating oil forms an arc shape due to the surface tension effect of the liquid and will not flow out easily. This surface tension allows the lubricating oil to be adsorbed and flow in the second dynamic flow channel. During the process of moving from the wide end to the narrow end, some lubricating oil will overflow, so that the second dynamic flow channel forms a liquid surface higher than the window beam facing the pocket, thereby reducing the impact potential energy and reducing frictional heat generation.

[0018] In the preferred implementation, the surface of the window beam facing the pocket is inclined, and the width of the pocket between adjacent window beams gradually narrows from the inner ring of the bearing to the outer ring of the bearing.

[0019] In a preferred implementation, the area of ​​the second dynamic flow channel is 10%-12% of the area of ​​the inclined plane, and the depth D satisfies 1mm≤D≤3mm.

[0020] When the area and depth of the second dynamic flow channel are higher than the design requirements, the structural strength of the cage is easily insufficient, and structural damage is easily caused when the cage rotates. When the area and depth of the second dynamic flow channel are lower than the design requirements, the lubricating oil in the second dynamic flow channel is too small, which easily causes wear and heat generation. When the area and depth of the oil chute are within the design requirements, the cage has good structural strength and can also play a good role in reducing impact and friction. Attached Figure Description

[0021] The accompanying drawings, which are included to provide a further understanding of the invention and form part of this invention, illustrate exemplary embodiments of the invention and, together with their description, serve to explain this application and do not constitute an undue limitation of the invention. In the drawings:

[0022] Figure 1 A schematic three-dimensional structural diagram of one embodiment of the high-flow dynamic lubrication tapered bearing cage of this application is shown;

[0023] Figure 2 This application is illustrated. Figure 1 An enlarged structural schematic diagram of one embodiment of part A in the diagram;

[0024] Label Explanation:

[0025] 10-Large end diameter ring; 11-Small end diameter ring; 12-Window beam; 120-Oil groove; 13-First dynamic flow channel; 130-Main flow channel; 1300-Oil cut-off section; 131-Branch flow channel; 14-Second dynamic flow channel. Detailed Implementation

[0026] In the following description, only certain exemplary embodiments are briefly described. As those skilled in the art will recognize, the described embodiments can be modified in various ways without departing from the spirit and scope of the invention. Therefore, the drawings and description are considered to be exemplary in nature and not restrictive.

[0027] The present invention will now be described with reference to the accompanying drawings.

[0028] The specific solution adopted is as follows:

[0029] like Figure 1-2 As shown, the present invention provides a high-flow dynamic lubrication tapered bearing cage, including a large end ring 10, a small end ring 11, and multiple window beams 12. The two ends of the window beams 12 are fixedly connected to the large end ring 10 and the small end ring 11, respectively. The multiple window beams 12 are evenly spaced along the circumference of the cage, and the adjacent window beams 12 form window holes for mounting rolling elements. A first dynamic flow channel 13 is provided on the inner ring surface of the window beams 12, and a second dynamic flow channel 14 is provided on the pocket surface of the window beams 12. During the high-speed rotation of the bearing, the lubricating oil can come from the first dynamic flow channel 13 to the second dynamic flow channel 14 and fill the second dynamic flow channel 14. When the rolling element moves toward the window beams 12, it can contact the lubricating oil in the second dynamic flow channel 14 to reduce the impact potential energy and reduce frictional heat generation.

[0030] The high-flow dynamic lubrication tapered bearing cage of this application has a first dynamic flow channel 13 opened on the cage beam 12 facing the inner ring of the bearing, and a second dynamic flow channel 14 opened on the beam 12 facing the pocket surface. The first dynamic flow channel 13 and the second dynamic flow channel 14 are connected. When the tapered bearing rotates at high speed, under the action of centrifugal force and inertial force, the grease or lubricating oil will move towards the larger end. When the lubricating oil accumulates from the smaller end to the larger end, the lubricating oil usually passes through the beam 12 surface. During the movement along the beam 12 surface, the lubricating oil in the first dynamic flow channel 13 can enter the second dynamic flow channel 14 and fill the entire second dynamic flow channel 14. When the rolling element moves towards the beam 12, it can contact the lubricating oil in the second dynamic flow channel. As a liquid buffer, it can reduce the impact potential energy of the rolling element. At the same time, it can absorb the frictional heat generated between the rolling element and the cage, reduce the cage temperature rise, and help protect the cage stability and improve the service life of the tapered bearing under complex load and high-speed rotation application conditions.

[0031] For the specific structure of the first dynamic flow channel 13, please refer to [link / details]. Figure 2 The first dynamic flow channel 13 includes a main flow channel 130 arranged along the length of the window beam 12 and a branch flow channel 131 connected to the main flow channel 130. The branch flow channel 131 is V-shaped, and the two inclined channels of the V-shaped branch flow channel 131 are distributed on both sides of the main flow channel 130, respectively connecting to the two second dynamic flow channels 14 facing the pocket surface of the window beam 12. The large opening of the branch flow channel 131 faces the small end diameter ring 11. This design allows the lubricating oil to flow into the branch flow channel 131 during the process of moving from the small end diameter ring 11 to the large end diameter ring 10 in the first dynamic flow channel 13, and then enter the second dynamic flow channel 14 from the branch flow channel 131.

[0032] As the first preferred embodiment of this implementation, in order to make the lubricating oil on the window beam 12 facing the pocket surface evenly distributed, so as to achieve better friction reduction, friction reduction and heat dissipation effects, in this embodiment, multiple branch channels 131 are provided at intervals along the length direction of the main channel 130, and multiple corresponding second dynamic channels 14 are provided, which are evenly spaced on the window beam 12 facing the pocket surface. The lubricating oil can be more evenly distributed between the cage and the rolling elements. The evenly distributed lubricating oil can effectively reduce the direct contact between the moving parts of the bearing and form a lubricating film, reducing friction and wear. This can ensure that the lubricating oil can fully lubricate the contact surface of the entire bearing system, reduce friction and wear, improve bearing life and performance. After the lubricating oil is evenly distributed, it can better absorb and dissipate heat, provide a cooling effect, avoid bearing overheating, and improve the stability and reliability of bearing operation.

[0033] As a second preferred embodiment of this implementation, when lubricating oil accumulates from the small end to the large end in the tapered roller bearing, the small end will be affected by insufficient lubrication, especially when the lubricating oil has poor flowability or uneven distribution. This may cause the lubricating film on the surface of the small end bearing to become thinner or interrupted, increasing the risk of friction and wear. The oil film thickness may be uneven in different parts of the roller, increasing local contact stress and wear risk. In order to reduce the above-mentioned effects and ensure that the lubricating oil can be evenly distributed to various parts inside the bearing when it is running at high speed, in this embodiment, the cross-sectional width of the main channel 130 gradually narrows from the small end diameter ring 11 to the large end diameter ring 10, so that the lubricating oil is subjected to gradually increasing resistance during movement, thereby reducing the amount of lubricating oil accumulating towards the large end. If a block is directly applied, the lubricating oil may have a large impact force on the window beam 12, which may disrupt the dynamic balance of the bearing operation and slow down the formation speed of the lubricating film on the roller surface.

[0034] As a third preferred embodiment under this implementation method, see Figure 2 The main channel 130 is provided with an oil interception section 1300. The oil interception section 1300 is a triangular-shaped area formed between the branch channel 131 and the main channel 130. When the lubricating grease moves along the main channel 130, part of it is intercepted in the oil interception section 1300, while part continues to move. The intercepted lubricating grease can enter the branch channel 131. The setting of the oil interception section 1300 can ensure that the branch channel 131 and the second dynamic channel 14 can enter with a sufficient amount of lubricating grease, and the structural design is more reasonable.

[0035] As a fourth preferred embodiment of this implementation, an oil groove 120 is provided at the junction of the window beam 12 with the large end diameter ring 10 and the small end diameter ring 11. The two ends of the main flow channel 130 are connected to the oil groove 120 through the branch flow channel 131 respectively. The V-shaped branch flow channel 131 close to the large end diameter ring 10 has its large opening facing the large end diameter ring 10.

[0036] The oil groove 120 at the junction of the window beam 12 and the end ring serves as an oil passage. This design allows for a certain gap at the window beam 12 of the cage, enabling lubricating oil to fully lubricate between the end ring and the window beam 12, ensuring stable rotation of the rolling elements. By designing the V-shaped branch channel 131 near the large end diameter ring 10 with its large opening facing the large end diameter ring 10, it is beneficial to guide the lubricating oil into the oil groove 120, reducing oil passage resistance and mitigating the impact of the lubricating oil on the window beam 12 under centrifugal and inertial forces during high-speed bearing operation.

[0037] As the fifth preferred embodiment under this implementation, the centerline of the second dynamic flow channel 14 and the centerline of the cage have an angle θ, which satisfies 45°≤θ≤90°.

[0038] When the included angle θ is within the range of 45°≤θ≤90°, the lubricating oil in the branch channel 131 is more likely to enter the second dynamic channel 14 under centrifugal throw when it reaches the junction of the branch channel 131 and the second dynamic channel 14. This is because when the lubricating oil at this position is thrown outward towards the outer ring of the bearing under centrifugal force, it will hit the inclined surface inside the second dynamic channel 14, making it difficult to be thrown out of the second dynamic channel 14. However, when the included angle θ is outside the range of 45°≤θ≤90°, when the lubricating oil in the branch channel 131 reaches the junction of the branch channel 131 and the second dynamic channel 14, under the action of centrifugal throw, there is no obstruction or the obstruction force is too large, causing most of the lubricating oil to leave the junction position and directly enter the outer ring position from the gap between the rolling element and the window beam 12. This results in too little lubricating oil in the second dynamic channel 14, which cannot form a liquid level higher than the surface of the window beam 12 facing the pocket, and thus cannot play the role of reducing impact potential energy and reducing frictional heat generation.

[0039] As a sixth preferred embodiment of this implementation, in order to make it easier for the lubricating oil in the second dynamic flow channel 14 to form a liquid level slightly higher than the surface of the window beam 12 facing the pocket, see [reference needed]. Figure 2 In this embodiment, the cross-sectional width of the second dynamic flow channel 14 gradually narrows from the inner ring of the bearing to the outer ring of the bearing, and the area of ​​the second dynamic flow channel 14 becomes narrower and narrower. The wide end connects to the branch flow channel 131. When the lubricating oil comes from the branch flow channel 131 to the wide end, it enters the narrow space. Due to the surface tension effect of the liquid, the lubricating oil forms an arc shape and will not flow out easily. This surface tension allows the lubricating oil to be adsorbed and flow in the second dynamic flow channel 14. During the process of moving from the wide end to the narrow end, some lubricating oil will overflow, so that the second dynamic flow channel 14 forms a liquid surface higher than the window beam 12 facing the pocket surface, thereby reducing the impact potential energy and reducing frictional heat generation.

[0040] As a preferred embodiment of this application, the surface of the window beam 12 facing the pocket is inclined, and the width of the pocket between adjacent window beams 12 gradually narrows from the inner ring of the bearing to the outer ring of the bearing, which can reduce the contact area between the rolling element and the surface of the window beam 12 facing the pocket and reduce the friction.

[0041] As a preferred embodiment, the area of ​​the second dynamic flow channel 14 is 10%-12% of the area of ​​the inclined surface, and the depth D satisfies 1mm≤D≤3mm.

[0042] When the area and depth of the second dynamic flow channel 14 are higher than the design requirements, the structural strength of the cage is easily insufficient, and structural damage is easily caused when the cage rotates. When the area and depth of the second dynamic flow channel 14 are lower than the design requirements, the lubricating oil in the second dynamic flow channel 14 is too small, which easily causes wear and heat generation. When the area and depth of the oil cutting groove are within the design requirements, the cage has good structural strength and can also play a good role in reducing impact and friction.

[0043] For any parts not mentioned in this invention, existing technologies can be used or referenced.

[0044] In the description of this invention, it should be understood that the terms "center," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," "outer," "axial," "radial," and "circumferential," etc., indicating orientation or positional relationships, are based on the orientation or positional relationships shown in the accompanying drawings and are only for the convenience of describing the invention and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of the invention. In this invention, unless otherwise expressly specified and limited, the first feature being "upper" or "lower" than the second feature can mean that the first and second features are in direct contact, or that the first and second features are in indirect contact through an intermediate medium.

[0045] In this invention, unless otherwise explicitly specified and limited, the terms "installation," "connection," "linking," and "fixing," etc., should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral unit; they can refer to a direct connection or an indirect connection through an intermediate medium; they can refer to the internal communication of two components or the interaction between two components. However, specifying a direct connection indicates that the two connected entities do not establish a connection relationship through an intermediate structure, but are simply connected to form a whole through a connecting structure. For those skilled in the art, the specific meaning of the above terms in this invention can be understood according to the specific circumstances.

[0046] In this invention, descriptions involving "first," "second," etc., are for descriptive purposes only and should not be construed as indicating or implying their relative importance or implicitly specifying the number of technical features indicated. Therefore, a feature defined with "first" or "second" may explicitly or implicitly include at least one of that feature.

[0047] The above are merely specific embodiments of the present invention, but the scope of protection of the present invention is not limited thereto. Any person skilled in the art can easily conceive of various variations or substitutions within the technical scope disclosed in the present invention, and these should all be included within the scope of protection of the present invention. Therefore, the scope of protection of the present invention should be determined by the scope of the claims.

Claims

1. A high-flow dynamic lubrication tapered bearing cage, comprising a large-end diameter ring, a small-end diameter ring, and multiple window beams, wherein the two ends of each window beam are fixedly connected to the large-end diameter ring and the small-end diameter ring, respectively, and the multiple window beams are evenly spaced along the circumferential direction of the cage, with adjacent window beams forming window holes for mounting rolling elements, characterized in that, The window beam has a first dynamic flow channel facing the inner ring of the bearing, and the window beam has a second dynamic flow channel facing the pocket. During the high-speed rotation of the bearing, the lubricating oil can come from the first dynamic flow channel to the second dynamic flow channel and fill the second dynamic flow channel. When the rolling element moves toward the window beam, it can contact the lubricating oil in the second dynamic flow channel to reduce the impact potential energy and reduce frictional heat generation. The first dynamic flow channel includes a main flow channel arranged along the length of the window beam and a branch flow channel connected to the main flow channel. The branch flow channel is V-shaped, with the large opening of the branch flow channel facing the small end diameter ring. The branch flow channel is connected to the second dynamic flow channel. The lubricating grease enters the branch flow channel as it moves from the small end diameter ring to the large end diameter ring in the first dynamic flow channel, and then enters the second dynamic flow channel from the branch flow channel. Multiple branch channels are provided at intervals along the length of the main channel, and multiple corresponding second dynamic channels are provided, evenly spaced on the window beam facing the pocket surface; the cross-sectional width of the main channel gradually narrows from the small end diameter ring to the large end diameter ring. The main flow channel is equipped with an oil interception section, which can intercept part of the lubricating oil moving along the main flow channel and allow it to enter the branch flow channel. An oil passage groove is provided at the junction of the window beam with the large end diameter ring and the small end diameter ring. The two ends of the main flow channel are connected to the oil passage groove through branch flow channels. The V-shaped branch flow channel near the large end diameter ring has its large opening facing the large end diameter ring.

2. The high-flow dynamic lubrication tapered bearing cage according to claim 1, characterized in that, The centerline of the second dynamic flow channel and the centerline of the cage have an angle θ, which satisfies 45°≤θ≤90°.

3. A high-flow dynamic lubrication tapered bearing cage according to claim 1, characterized in that, The cross-sectional width of the second dynamic flow channel gradually narrows from the inner ring of the bearing to the outer ring of the bearing, and the wide end connects to the branch flow channel.

4. A high-flow dynamic lubrication tapered bearing cage according to claim 1, characterized in that, The surface of the window beam facing the pocket is sloping, and the width of the pocket between adjacent window beams gradually narrows from the inner ring of the bearing to the outer ring of the bearing.

5. A high-flow dynamic lubrication tapered bearing cage according to claim 4, characterized in that, The area of ​​the second dynamic flow channel is 10%-12% of the area of ​​the inclined plane, and the depth D satisfies 1mm≤D≤3mm.

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