Weight reduction type cylindrical roller bearing retainer

Abstract

The utility model discloses a weight reduction type cylindrical roller bearing retainer which comprises a first end ring, a second end ring and window beams, the first end ring and the second end ring are symmetrical, the window beams are evenly distributed between the first end ring and the second end ring at intervals, the ring width of the first end ring and the second end ring is larger than the section thickness of the window beams, and the first end ring and the second end ring are provided with limiting protruding points. When moving towards the window beam, the rollers can make contact with the limiting protruding points so as to be limited from further impacting the window beam, the window beam is arranged in a sheet mode, the section thickness of the limiting protruding points is larger than that of the window beam, the overall weight is reduced through the sheet arrangement of the window beam, and the overall weight is reduced through the sheet arrangement of the window beam. The rollers can be in contact with the limiting salient points when moving towards the window beam, so that the rollers are prevented from further impacting the window beam, direct collision between the rollers and the window beam is prevented, the frequency and strength of dynamic collision are reduced, the service life of the retainer is prolonged, and the service life of the retainer is prolonged. And the requirements of high-speed running fields such as new energy automobiles which pursue lightweight design are met.

Description

Technical Field

[0001] This application belongs to the field of bearing cages, and particularly relates to a heavy-duty cylindrical roller bearing cage. Background Technology

[0002] In the application scenarios of new energy vehicles, the fatigue fracture problem of cylindrical cages is becoming increasingly serious. Due to the characteristics of the power system of new energy vehicles, the bearings of their output shafts need to withstand complex operating conditions of high-speed operation and frequent deceleration. Under these conditions, the difference in rotational speed between the rolling elements and the cage cannot be completely eliminated, leading to frequent dynamic collisions between them. These dynamic collisions exacerbate the stress concentration phenomenon inside the bearing. Over time, specific areas of the cage, such as the corners of the pocket window beams, will gradually develop fatigue damage due to continuous stress accumulation. Once the fatigue limit of the material is exceeded, fatigue fracture will occur, seriously affecting the service life of the bearing and the overall performance of the new energy vehicle.

[0003] To address this issue, current designs generally tend to increase the overall thickness of the window beam to enhance the structural strength of the cage and improve its resistance to fatigue fracture. However, while this solution is effective, it also has side effects, namely a significant increase in the weight of the cage and even the entire bearing. In high-speed operating fields such as new energy vehicles, where lightweight design is pursued, this increased weight becomes a disadvantage, not only increasing energy consumption but also potentially affecting the bearing's operating efficiency and lifespan.

[0004] Therefore, how to reduce the weight of the cage by optimizing its design while ensuring its strength, so as to avoid various problems caused by excessive weight, and at the same time effectively prevent fatigue fracture caused by lightweight design, has become an important research direction in the field of bearing design. Utility Model Content

[0005] This invention provides a lightweight cylindrical roller bearing cage that enhances structural strength to prevent fatigue fracture while reducing weight to avoid increased energy consumption and reduced operating efficiency.

[0006] To achieve the above objectives, the present invention provides the following technical solution:

[0007] A lightweight cylindrical roller bearing cage includes symmetrical first and second end rings and window beams evenly spaced between them. Adjacent window beams form pockets for rollers to be inserted. The ring width of the first and second end rings is greater than the cross-sectional thickness of the window beams. The first and second end rings are provided with limiting protrusions. When the rollers move toward the window beams, they can contact the limiting protrusions to limit further impact of the rollers onto the window beams. The window beams are thinned and the cross-sectional thickness of the limiting protrusions is greater than the cross-sectional thickness of the window beams, thereby achieving local reinforcement of the impact area and reducing the overall weight of the cage.

[0008] The aforementioned structure, with its thinner window beam design reducing overall weight, features a greater cross-sectional thickness at the limiting protrusions than the window beam itself. This achieves localized reinforcement at the impact point. When the roller moves towards the window beam, it contacts the limiting protrusions, thus limiting further impact and preventing direct collisions between the roller and the window beam. This reduces the frequency and intensity of dynamic collisions, contributing to extended cage lifespan and meeting the requirements of high-speed operating fields such as new energy vehicles that prioritize lightweight design. Lightweight design helps reduce energy consumption, improves bearing operating efficiency and lifespan, and effectively reduces the risk of fatigue fracture through structural features such as localized reinforcement and limiting roller impact, while simultaneously meeting lightweight requirements.

[0009] In a preferred implementation, grooves are provided at the center of both the upper and lower surfaces of the roller, and the limiting protrusions are connected to the grooves, allowing the roller to rotate relative to the limiting protrusions.

[0010] The combination of the groove and the limiting protrusion can prevent the roller from shifting too much during operation, thus maintaining the stable position of the roller in the bearing. At the same time, it allows the roller to rotate relative to the limiting protrusion within a certain range, preventing unnecessary collisions between the roller and the thinned window beam of the cage, and reducing the risk of stress concentration and fatigue damage.

[0011] In the preferred implementation, the width W1 of the window beam and the width W2 of the pocket satisfy the condition that W2≤W1≤2W2.

[0012] Increasing the width of the window beam can compensate for the reduction in material thickness to some extent. A wider window beam can provide a larger cross-sectional area, thereby increasing its resistance to deformation and fracture.

[0013] In a preferred embodiment, the window beam is integrally formed with the first end ring and the second end ring, and the three have the same cross-sectional thickness.

[0014] The one-piece design enhances the connection strength between the window beam and the end ring, giving the entire cage better integrity and stability when bearing roller loads. The window beam, the first end ring, and the second end ring have the same cross-sectional thickness, which helps to maintain the uniformity and balance of the entire cage under stress, resulting in an overall lightweight design.

[0015] In a preferred embodiment, the window beam is riveted to the first end ring / second end ring, and multiple pieces of the window beam are arranged radially at intervals to enhance load-bearing capacity.

[0016] In a preferred implementation, the window beam is provided with at least one first weight-reducing hole.

[0017] In a preferred embodiment, the first end ring and the second end ring are provided with second weight-reducing holes, and a plurality of second weight-reducing holes are evenly arranged circumferentially.

[0018] In a preferred embodiment, the window beam is disposed near the inner diameter surface of the first end ring and the second end ring, and the second weight-reducing hole is disposed near the outer diameter surface of the first end ring and the second end ring or is disposed between the inner diameter surface and the outer diameter surface.

[0019] In a preferred implementation, the second weight-reducing hole corresponds radially to the window beam or pocket. Attached Figure Description

[0020] The accompanying drawings, which are included to provide a further understanding of the present invention and constitute a part of this invention, illustrate exemplary embodiments of the present invention and, together with the description thereof, serve to explain this application and do not constitute an undue limitation of the present invention. In the drawings:

[0021] Figure 1 A schematic three-dimensional structural diagram of one embodiment of the heavy-duty cylindrical roller bearing cage of this application is shown;

[0022] Figure 2 A schematic diagram illustrating one embodiment of the limiting protrusion of this application is shown.

[0023] Figure 3 A schematic cross-sectional view of one embodiment of the cylindrical roller of this application is shown;

[0024] Figure 4 A schematic diagram illustrating one embodiment of the thin-film window beam of this application is shown;

[0025] Label Explanation:

[0026] 10-First end ring; 11-Second end ring; 12-Window beam; 13-Pocket; 14-Limiting protrusion; 15-Roller; 150-Groove; 16-First weight-reducing hole; 17-Second weight-reducing hole. Detailed Implementation

[0027] 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 this invention. Therefore, the drawings and description are considered exemplary in nature and not restrictive.

[0028] In the description of this utility model, 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 the orientation or positional relationship, are based on the orientation or positional relationship shown in the accompanying drawings and are only for the convenience of describing this utility model 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 this utility model. In this utility model, 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.

[0029] In this utility model, unless otherwise explicitly specified and limited, the terms "installation," "connection," "joining," 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 main bodies at the connection point are not connected by 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 utility model can be understood according to the specific circumstances.

[0030] In this utility model, 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.

[0031] The present invention will now be described with reference to the accompanying drawings.

[0032] The specific solution adopted is as follows:

[0033] like Figure 1-4 As shown, this utility model provides a lightweight cylindrical roller bearing cage, including a symmetrical first end ring 10 and a second end ring 11, and window beams 12 evenly spaced between them. Adjacent window beams form pockets 13 for rollers to be inserted. The ring width of the first end ring and the second end ring is greater than the cross-sectional thickness of the window beams. The first end ring and the second end ring are provided with limiting protrusions 14. When the rollers move toward the window beams, they can contact the limiting protrusions to limit the rollers 15 from further impacting the window beams. The window beams are thinned and the cross-sectional thickness of the limiting protrusions is greater than the cross-sectional thickness of the window beams, thereby achieving local reinforcement of the impact area and reducing the total weight of the cage.

[0034] The above structure reduces the overall weight by making the window beam thinner, but the cross-sectional thickness of the limiting protrusion is greater than that of the window beam, which achieves local reinforcement of the impact area. When the roller moves toward the window beam, it can contact the limiting protrusion, thereby limiting the roller from further impacting the window beam, preventing direct collision between the roller and the window beam, reducing the frequency and intensity of dynamic collisions, and helping to extend the service life of the cage.

[0035] The thinner design of the window beam 12 significantly reduces the overall weight of the cage, meeting the requirements of high-speed operating fields such as new energy vehicles that pursue lightweight design. Lightweight design helps reduce energy consumption burden, improve bearing operating efficiency and life, and effectively reduces the risk of fatigue fracture through structural features such as local reinforcement and limiting roller impact, while simultaneously meeting the lightweight requirements.

[0036] In a preferred embodiment of this application, grooves are provided at the center of both the upper and lower surfaces of the roller, and the limiting protrusions are connected to the grooves, allowing the roller to rotate relative to the limiting protrusions.

[0037] The combination of the groove and the limiting protrusion prevents the roller from shifting too much during operation, thus maintaining the roller's stable position within the bearing. It also allows the roller to rotate relative to the limiting protrusion within a certain range, helping it better adapt to dynamic changes within the bearing. This maintains good contact and lubrication between the roller and the inner and outer rings, prevents unnecessary collisions between the roller and the thinned cage beam, and reduces the risk of stress concentration and fatigue damage. When the roller is confined to a specific position, its running trajectory is more stable, reducing vibration and noise caused by positional uncertainty, and contributing to improved bearing smoothness and overall performance.

[0038] In addition, see Figure 1 and Figure 3 The design features a long and a short limiting protrusion, and correspondingly, a deep and a shallow groove. The long limiting protrusion can serve as a guide during assembly. During assembly, the upper surface of the roller is brought close to the lower surface of the upper end ring, and then the roller is lowered so that the short limiting protrusion enters the groove on the lower side of the roller, thus achieving the installation and limiting of the roller.

[0039] In a preferred embodiment of this application, the width W1 of the window beam and the width W2 of the pocket satisfy W2≤W1≤2W2. The window beam is thinned to reduce weight, but by increasing its width (W1), the reduction in material thickness can be compensated to some extent. A wider window beam can provide a larger cross-sectional area, thereby increasing its resistance to deformation and fracture.

[0040] When W1 equals W2, it means the width of the window sill is exactly the same as the width of the pocket. In this case, although the number of rollers is maximized, the structural strength of the window sill will be affected to some extent. A window sill that is too narrow cannot provide sufficient support and stability, especially when subjected to heavy loads or high-speed operation.

[0041] When W1 equals 2W2, the width of the lintel is twice the width of the pocket. In this case, the lintel has a larger width and greater structural strength, better supporting the rollers and preventing them from deforming or being damaged. However, an excessively wide lintel reduces the number of pockets, thus reducing the number of rollers, which affects the bearing's load-bearing capacity and operational smoothness. In practical designs, an optimal range between W2 and 2W2 is usually chosen. This range is neither too large nor too small, ensuring a sufficient number of rollers to provide adequate load-bearing capacity while enhancing the structural strength of the lintel to improve the bearing's stability and durability.

[0042] As a preferred embodiment of this application, the window beam, the first end ring, and the second end ring are integrally formed, and the three have the same cross-sectional thickness. The integral forming design enhances the connection strength between the window beam and the end ring, so that the entire cage has better integrity and stability when bearing roller loads. The window beam, the first end ring, and the second end ring have the same cross-sectional thickness, which helps to maintain the uniformity and balance of the entire cage under stress, resulting in an overall lightweight design.

[0043] In a preferred embodiment of this application, the window beam is riveted to the first end ring / second end ring, and multiple pieces of the window beam are arranged radially at intervals to enhance the load-bearing performance. The window beam and the end ring are tightly connected together by rivets to form an integral structure, which helps to improve the overall stability and load-bearing capacity. The thin window beam with multiple pieces arranged radially at intervals can improve the overall load-bearing capacity of the window beam.

[0044] In a preferred embodiment of this application, the window beam is provided with at least one first weight-reducing hole 16, which can further reduce the weight of the window beam, thereby reducing the weight of the overall structure. By reasonably arranging the weight-reducing holes, the structural performance of the window beam can be optimized without sacrificing structural strength. The shape and size of the weight-reducing holes can be designed according to actual needs. The shapes include circles, ellipses, rectangles, etc. In terms of size, the size of the weight-reducing holes should be determined according to the thickness of the window beam and the load-bearing requirements.

[0045] In a preferred embodiment of this application, the first end ring and the second end ring are provided with a second weight-reducing hole, and a plurality of second weight-reducing holes are evenly arranged circumferentially. By providing weight-reducing holes on the second end ring and the first end ring, the weight of the end ring component can be effectively reduced, thereby reducing the moment of inertia during rotation and improving mechanical efficiency. The design of the weight-reducing hole also facilitates lubrication and heat dissipation, especially in high-power or high-speed applications, where this advantage is particularly significant.

[0046] Furthermore, the window beam is positioned near the inner diameter surface of the first and second end rings, and the second weight-reducing hole 17 is positioned near the outer diameter surface of the first and second end rings, or located between the inner and outer diameter surfaces. Additionally, the second weight-reducing hole corresponds radially to the window beam or pocket. Positioning the second weight-reducing hole near the outer diameter surface of the end rings or between the inner and outer diameter surfaces ensures a sufficiently large connection area between the window beam and the end rings, thereby providing adequate connection strength. The placement of the weight-reducing hole is carefully planned to avoid weakening critical connection areas, ensuring the stability and safety of the overall structure. When the second weight-reducing hole corresponds radially to the window beam or pocket, a smoother lubrication channel is formed, helping the lubricant to penetrate more effectively into the contact area between the rollers and raceways, thus improving the lubrication effect.

[0047] For any parts not mentioned in this utility model, existing technologies can be used or referenced.

[0048] The above are merely specific embodiments of this utility model, but the protection scope of this utility model is not limited thereto. Any person skilled in the art can easily conceive of various variations or substitutions within the technical scope disclosed in this utility model, and these should all be included within the protection scope of this utility model. Therefore, the protection scope of this utility model should be determined by the scope of the claims.

Claims

1. A lightweight cylindrical roller bearing cage, characterized in that, It includes a symmetrical first end ring and a second end ring, and window beams evenly spaced between them. Adjacent window beams form pockets for rollers to be inserted. The ring width of the first end ring and the second end ring is greater than the cross-sectional thickness of the window beam. The first end ring and the second end ring are provided with limiting protrusions. When the roller moves toward the window beam, it can contact the limiting protrusions to limit the roller from further impacting the window beam. The window beam is thinned and the cross-sectional thickness of the limiting protrusions is greater than the cross-sectional thickness of the window beam, thereby achieving local reinforcement of the impact area and reducing the total weight of the cage.

2. The heavy-duty cylindrical roller bearing cage according to claim 1, characterized in that, The upper and lower surfaces of the roller are both provided with grooves at their centers, and the limiting protrusions are connected to the grooves, allowing the roller to rotate relative to the limiting protrusions.

3. The heavy-duty cylindrical roller bearing cage according to claim 1, characterized in that, The width W1 of the window beam and the width W2 of the pocket satisfy the condition that W2≤W1≤2W2.

4. The heavy-duty cylindrical roller bearing cage according to claim 1, characterized in that, The window beam is integrally formed with the first end ring and the second end ring, and the three have the same cross-sectional thickness.

5. The heavy-duty cylindrical roller bearing cage according to claim 1, characterized in that, The window beam is riveted to the first end ring / second end ring, and multiple pieces of the window beam are arranged radially at intervals to enhance load-bearing capacity.

6. The heavy-duty cylindrical roller bearing cage according to claim 4 or 5, characterized in that, The window beam is provided with at least one first weight-reducing hole.

7. The reduced-weight cylindrical roller bearing cage according to claim 4 or 5, characterized in that, The first end ring and the second end ring are provided with second weight reduction holes, and multiple second weight reduction holes are evenly arranged circumferentially.

8. The heavy-duty cylindrical roller bearing cage according to claim 7, characterized in that, The window beam is located near the inner diameter surface of the first end ring and the second end ring, and the second weight-reducing hole is located near the outer diameter surface of the first end ring and the second end ring or between the inner diameter surface and the outer diameter surface.

9. The heavy-duty cylindrical roller bearing cage according to claim 8, characterized in that, The second weight-reducing hole corresponds radially to the window beam or pocket.

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