High-strength integrally-formed retainer

Abstract

The utility model discloses a high-strength integrally-formed retainer which comprises a retainer body, the retainer body comprises an end ring, the end ring is molded into a plurality of wave crest sections and wave trough sections which are evenly spaced through stamping, each wave trough section is located between every two adjacent wave crest sections, and the end ring is directly formed into the wave crest sections and the wave trough sections in a stamping molding mode; meanwhile, the pocket holes are naturally formed by the bent parts of the wave crest sections and the wave trough sections, additional punching or cutting procedures are not needed, the production process is greatly simplified, the precision and consistency of the wave crest sections, the wave trough sections and the bent parts can be ensured by accurately controlling the shape and size of a stamping die, and therefore the high requirement of the retainer for precision is met; due to the fact that complex cutting and punching procedures are avoided, the problem of abrasion of the cutter is remarkably solved. Therefore, the production cost is reduced, and the stability and reliability of the production line are improved.

Description

Technical Field

[0001] This application belongs to the field of bearings, and particularly relates to a high-strength integrally formed cage. Background Art

[0002] As a key component of a bearing, the core function of the cage is to effectively wrap and separate the rolling elements, avoiding direct contact between them, thereby significantly reducing friction and wear and extending the service life of the bearing. The manufacturing process of traditional cages often involves a series of complex technological steps, such as cutting, forming, punching, and fine machining of the pocket grooves. Among them, the machining of the pocket grooves is particularly crucial but also extremely challenging, as it requires extremely high precision and stability to ensure the smoothness and width consistency of the groove openings and avoid rapid wear or breakage of the cutting tools. In contrast, a cage design consisting of two end rings and several struts avoids the complex pocket groove machining process and firmly connects the end rings and struts through riveting or other assembly methods to form a stable support structure. However, although the complex process of punching pocket grooves is avoided, the riveting assembly step also has an efficiency bottleneck. Although this design simplifies part of the manufacturing process, the riveting process introduces new assembly errors, so the overall production efficiency has not been significantly improved. In view of the above analysis, it is particularly important to design a new type of cage for more efficient production. Thus, the existing technology needs to be further improved and enhanced. Content of the Utility Model

[0003] The utility model provides a high-strength integrally formed cage to at least solve or alleviate one or more technical problems in the prior art, or at least provide a beneficial alternative.

[0004] To achieve the above object, the utility model provides the following technical solutions:

[0005] A high-strength integrally formed cage includes a cage body. The cage body includes end rings, and the end rings are shaped by stamping into several uniformly spaced wave crest segments and wave trough segments. Among them, the wave trough segments are located between two adjacent wave crest segments. The wave crest segments include a first wave crest segment, a second wave crest segment, and an arc segment connecting the ends of the two. The first wave crest segment and the second wave crest segment are perpendicular to the wave trough segment. The wave crest segments form the window beams of the cage body. The ends of the wave crest segments are bent to form bending parts, and the bending parts, together with the wave crest segments and wave trough segments on both sides, form pockets for accommodating cylindrical rolling elements, so as to simplify the production process and improve production efficiency.

[0006] The high-strength integrally formed cage of the present application directly forms the wave crest section and the wave trough section of the end ring through stamping and shaping. At the same time, the bending part of the wave crest section and the wave trough section naturally form the pocket without additional punching or cutting processes, greatly simplifying the production process. By precisely controlling the shape and size of the stamping die, the accuracy and consistency of the wave crest section, the wave trough section, and the bending part can be ensured, thus meeting the high requirements for the accuracy of the cage. Since complex cutting and punching processes are avoided, the tool wear problem is significantly improved. This not only reduces the production cost but also improves the stability and reliability of the production line. The integrally formed production method reduces the separate processing and subsequent assembly steps of multiple components, making the entire production process more compact and efficient. The simplified production process and efficient processing method significantly shorten the production cycle of the cage, helping the enterprise to quickly respond to market demands and improve market competitiveness.

[0007] In a preferred implementation, the length l of the bending part satisfies 1 / 2 rolling element diameter ≤ l ≤ rolling element diameter.

[0008] Setting the length l of the bending part within the range of 1 / 2 rolling element diameter ≤ l ≤ rolling element diameter can effectively limit the upward movement of the rolling element and prevent it from being thrown out, and can also minimize the cost.

[0009] In a preferred implementation, there is a clearance space between the bending part cylinder and the upper plane of the rolling element to enable the cylindrical rolling element to rotate within the pocket.

[0010] In a preferred implementation, the end of any one bending part corresponds to the tail of the adjacent bending part to form a continuous closed-loop pocket.

[0011] In a preferred implementation, there is an oil passage clearance between the first wave crest section and the second wave crest section.

[0012] When the bearing rotates at high speed, the lubricating oil will rush towards the wave crest section due to the centrifugal force. The oil passage clearance can reduce this impact force and protect the wave crest section from damage. And when the roller impacts the wave crest section, the oil passage clearance provides a certain buffer space, allowing the wave crest section to undergo a certain amount of elastic deformation, thereby absorbing the impact energy and reducing noise and vibration.

[0013] In a preferred implementation, the oil passage clearance d satisfies 1 / 2 the thickness of the first wave crest section / second wave crest section ≤ d ≤ the thickness of the first wave crest section / second wave crest section.

[0014] In a preferred implementation, the width w of the wave crest section satisfies 1 / 3 rolling element diameter ≤ w ≤ 1 / 2 rolling element diameter.

[0015] Avoid having too small a contact area with the rolling elements in the wave crest section within this range, which may lead to insufficient strength or stiffness. At the same time, prevent the wave crest section from being too wide. If the wave crest section is too wide, it will increase the contact area with the rolling elements, increase unnecessary friction, and also increase the material consumption.

[0016] In a preferred implementation, the transition position between the wave crest section and the wave trough section is a rounded corner transition.

[0017] In a preferred implementation, the wave crest section is provided with an arc-shaped contact surface that contacts the arc-shaped surface of the cylindrical roller. Description of the Drawings

[0018] The drawings described herein are used to provide a further understanding of the present invention and form a part of the present invention. The schematic embodiments of the present invention and their descriptions are used to explain the present application and do not constitute an improper limitation to the present invention. In the drawings:

[0019] Figure 1 It shows a schematic structural diagram of a preferred implementation mode of the high-strength integrally formed cage of the present application before bending;

[0020] Figure 2 It shows a schematic structural diagram of a preferred implementation mode of the high-strength integrally formed cage of the present application after bending;

[0021] Figure 3 It shows a schematic structural diagram of a preferred implementation mode of the high-strength integrally formed cage of the present application assembled with cylindrical rollers;

[0022] Reference Numeral Description:

[0023] 10 - wave crest section; 100 - first wave crest section; 101 - second wave crest section; 102 - arc section; 103 - bending part; 11 - wave trough section; 2 - pocket. Detailed Embodiments

[0024] In the following, only some exemplary embodiments are simply described. As those skilled in the art can recognize, the described embodiments can be modified in various different ways without departing from the spirit and scope of the present invention. Therefore, the drawings and the description are considered to be exemplary in nature rather than restrictive.

[0025] In the description of the present utility model, it should be understood that the orientation or positional relationship indicated by terms such as "center", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "axial", "radial", "circumferential", etc. is based on the orientation or positional relationship shown in the drawings. It is only for the convenience of describing the present utility model and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation. Therefore, it should not be construed as a limitation to the present utility model. In the present utility model, unless otherwise clearly specified and defined, the first feature being "on" or "under" the second feature may be that the first and second features are in direct contact, or the first and second features are indirectly in contact through an intermediate medium.

[0026] In the present utility model, unless otherwise clearly specified and defined, terms such as "installation", "connection", "connection", "fixation", etc. should be understood in a broad sense. For example, it can be a fixed connection, a detachable connection, or integrated; it can be directly connected, or indirectly connected through an intermediate medium, and can be the communication inside two elements or the interaction relationship between two elements. However, indicating a direct connection means that there is no connection relationship constructed through an excessive structure between the two connected main bodies, and they are only connected through the connection structure to form a whole. For those of ordinary skill in the art, the specific meanings of the above terms in the present utility model can be understood according to specific circumstances.

[0027] In the present utility model, descriptions such as "first", "second", etc. are only for descriptive purposes and should not be understood as indicating or implying their relative importance or implicitly indicating the quantity of the indicated technical features. Thus, features defined with "first", "second" may explicitly or implicitly include at least one such feature.

[0028] The following describes the present utility model in conjunction with the drawings of the specification.

[0029] The specific solution adopted is:

[0030] As Figures 1 - 3 shown, the present utility model provides a high-strength integrally formed cage, including a cage body. The cage body includes end rings. The end rings are shaped by stamping into several uniformly spaced wave crest segments 10 and wave trough segments 11. The wave trough segments are located between two adjacent wave crest segments. The wave crest segments include a first wave crest segment 100, a second wave crest segment 101, and an arc segment 102 connecting the ends of the two. The first wave crest segment and the second wave crest segment are perpendicular to the wave trough segment. The wave crest segments form the window beams of the cage body. The ends of the wave crest segments are bent to form bending portions 103. The bending portions and the wave crest segments and wave trough segments on both sides form pockets for accommodating cylindrical rolling elements, so as to simplify the production process and improve production efficiency.

[0031] During the manufacturing process of traditional cages, the machining of the pocket grooves is a complex and time-consuming process. In this design, by means of stamping and shaping, the end rings are directly formed into wave crest segments and wave trough segments. At the same time, the bending parts of the wave crest segments and the wave trough segments naturally form the pockets without additional punching or cutting processes, greatly simplifying the production process. By precisely controlling the shape and size of the stamping die, the accuracy and consistency of the wave crest segments, wave trough segments and bending parts can be ensured, thus meeting the high requirements for accuracy of the cage. Since complex cutting and punching processes are avoided, the tool wear problem is significantly improved. This not only reduces the production cost, but also improves the stability and reliability of the production line. The one-piece forming production method reduces the separate machining and subsequent assembly steps of multiple components, making the whole production process more compact and efficient. The simplified production process and efficient machining method significantly shorten the production cycle of the cage, which helps enterprises quickly respond to market demands and improve market competitiveness.

[0032] For cylindrical rollers, the vertical wave crest segments serve as window beams to provide more precise guidance and restraint, enabling the rolling elements to roll smoothly along the predetermined trajectory, reducing unnecessary friction and wear. The arc segments between the wave crest segments can produce certain elastic deformation when the window beams are subjected to forces and torques, thereby dispersing and absorbing these forces and reducing the impact and damage to the overall cage. The design of the wave crest segments, wave trough segments and arc segments makes this new type of cage excellent in terms of stability, adaptability and flexibility.

[0033] As a preferred embodiment of the present application, the length l of the bending part 103 satisfies 1 / 2 of the rolling element diameter ≤ l ≤ the rolling element diameter.

[0034] When the length l of the bending part is less than half of the rolling element diameter, when the rolling element is subjected to external forces (such as centrifugal force, vibration, etc.), the upward movement space will be relatively large. This increases the risk of the rolling element being thrown out of the cage, especially under the working conditions of high-speed rotation or impact.

[0035] Therefore, setting the lower limit to half of the rolling element diameter can ensure that the rolling elements can still be effectively restricted within the cage when subjected to a certain external force, preventing them from being thrown out. The length l of the bent portion should not be too long to avoid overly restricting the movement of the rolling elements. If l exceeds the diameter of the rolling elements, although it can ensure that the rolling elements will not be thrown out, it will increase the production material consumption. Setting the length l of the bent portion within the range of 1 / 2 rolling element diameter ≤ l ≤ rolling element diameter can not only effectively restrict the upward movement of the rolling elements and prevent them from being thrown out, but also minimize costs. At the same time, when the length l of the bent portion is equal to the diameter of the rolling elements, adjacent bent portions will almost come into contact with each other or be very close, thus forming a support between adjacent window beams. When the length l of the bent portion is set to 1 / 2 of the rolling element diameter, the upper lubricating surface of the rolling elements will also increase accordingly. A larger lubricating surface helps to form a more stable lubricating oil film, reducing the direct contact and friction surface between the rolling elements and the cage, thereby reducing wear and heat generation.

[0036] As a preferred embodiment of the present application, there is a clearance space between the bent portion 103 and the upper plane of the cylindrical rolling element, so that the cylindrical rolling element can rotate within the pocket. The clearance space allows the cylindrical rolling element to rotate smoothly within the pocket when subjected to an external force (such as a rotational torque). This is the basis for the normal operation of the bearing, and the clearance space also provides space for the presence of lubricating oil or grease. The lubricating oil film can fill the tiny gap between the rolling element and the bent portion, reducing direct contact and friction, thereby reducing wear and heat generation.

[0037] As a preferred embodiment of the present application, refer to Figure 2 , the end of any bent portion 103 corresponds to the tail of the adjacent bent portion to form a continuous closed-loop pocket. Specifically, keeping all the bent portions bent in the same direction (clockwise or counterclockwise) can ensure that the pocket forms a continuous closed-loop structure in three-dimensional space. This consistency not only simplifies the manufacturing process but also improves the overall strength and stiffness of the cage. The vertically projected bent portion after bending is on the trough section and at the center position of the cylindrical roller. This facilitates the installation of the inner and outer rings of the bearing and prevents interference between the bent portion and the inner and outer rings. When the contact point between the bent portion and the rolling element is near the center of the rolling element, the friction and wear caused by the eccentricity of the rolling element can be reduced. This is because during the rotation of the rolling element, its center position is relatively stable and not prone to large radial displacements.

[0038] As a preferred embodiment of the present application, there is an oil passage clearance between the first peak section 100 and the second peak section 101. Further, the oil passage clearance d satisfies 1 / 2 thickness of the first peak section / second peak section ≤ d ≤ thickness of the first peak section / second peak section. When the bearing rotates at high speed, the lubricating oil will rush towards the peak section due to the centrifugal force. The oil passage clearance d can reduce this impact force and protect the peak section from damage.

[0039] When the roller impacts the peak section, the oil passage clearance d provides a certain buffer space, allowing the peak section to undergo a certain amount of elastic deformation, thereby absorbing the impact energy and reducing noise and vibration.

[0040] The lower limit of d is set to half of the thickness of the peak section to ensure there is enough space for the lubricating oil to flow and to allow the peak section to undergo a certain degree of elastic deformation when subjected to impact. The upper limit of d is set to the thickness of the peak section, taking into account the machining accuracy and the stability of the peak section. If d is too large, the peak section will become unstable due to lack of sufficient support and is prone to deformation or damage when subjected to impact.

[0041] As a preferred embodiment of the present application, the width w of the peak section satisfies 1 / 3 of the rolling element diameter ≤ w ≤ 1 / 2 of the rolling element diameter. This range avoids too small a contact area with the rolling elements of the peak section, resulting in insufficient strength or stiffness. At the same time, it also prevents the peak section from being too wide. If the peak section is too wide, it will increase the contact area with the rolling elements, increase unnecessary friction, and also increase the material usage, causing unnecessary waste.

[0042] As a preferred embodiment of the present application, the transition position between the peak section and the valley section 11 is a rounded corner transition. The rounded corner transition can effectively reduce the stress concentration phenomenon at the junction of the peak and the valley. In the process of metal processing or forming, sharp corners often lead to stress concentration, increasing the risk of material cracking or damage. The rounded corner transition can disperse these stresses, making the structure more stable; the rounded corner transition can enhance the structural strength at the junction of the peak and the valley. Since the rounded corner transition disperses the stresses, this area can withstand greater loads and is not easily damaged, which is of great significance for improving the load-bearing capacity and stability of the entire structure.

[0043] As a preferred embodiment of the present application, the peak section is provided with an arc-shaped contact surface that contacts the arc-shaped surface of the cylindrical roller. The arc-shaped contact surface can ensure that the contact between the peak section and the cylindrical roller is more uniform and continuous, thereby reducing the friction and wear caused by poor contact. This helps to extend the service life of the components and reduce the maintenance cost. During the stamping process, only a corresponding arc-shaped die needs to be designed to form the required arc-shaped contact surface on the peak section. This die design is relatively simple and easy to manufacture and maintain.

[0044] What is not described in this utility model can be realized by adopting or referring to the existing technologies.

[0045] The above are only the specific embodiments of the present utility model, but the protection scope of the present utility model is not limited thereto. Any person skilled in the art within the technical scope disclosed by the present utility model can easily conceive of various changes or substitutions thereof, and these should all be covered within the protection scope of the present utility model. Therefore, the protection scope of the present utility model shall be subject to the protection scope of the claims.

Claims

1. A high-strength integrally formed retainer, characterized in that: The invention comprises a retainer body, which comprises an end ring, and the end ring is shaped into a plurality of evenly spaced peak sections and trough sections by stamping, wherein the trough section is located between two adjacent peak sections, and the peak section comprises a first peak section, a second peak section and an arc section connecting the ends of the two peak sections, and the first peak section and the second peak section are perpendicular to the trough section, and the peak section constitutes a window beam of the retainer body, and the end of the peak section is bent to form a bending portion, and a pocket for accommodating a cylindrical rolling body is formed between the bending portion and the peak sections and the trough sections on both sides, so as to simplify the production process and improve the production efficiency.

2. The high-strength integrally formed retainer according to claim 1, characterized in that: The length l of the bending portion satisfies the condition that 1 / 2 rolling element diameter ≤ l ≤ rolling element diameter.

3. The high-strength integrally formed retainer according to claim 1, characterized in that: There is a gap between the bent cylinder and the upper plane of the rolling body, so that the cylindrical rolling body can rotate in the pocket.

4. The high-strength integrally formed retainer according to claim 1, characterized in that: The end of any bent portion corresponds to the tail of the adjacent bent portion to form a continuous closed loop pocket.

5. The high-strength integrally formed retainer according to claim 1, characterized in that: There is an oil gap between the first wave crest section and the second wave crest section.

6. The high-strength integrally formed retainer according to claim 1, characterized in that: The oil-through gap d satisfies that 1 / 2 the thickness of the first wave peak section / the second wave peak section ≤ d ≤ the thickness of the first wave peak section / the second wave peak section.

7. The high-strength integrally formed retainer according to claim 1, characterized in that: The width w of the peak section satisfies the condition that 1 / 3 of the rolling element diameter ≤ w ≤ 1 / 2 of the rolling element diameter.

8. The high-strength integrally formed retainer according to claim 1, characterized in that: The intersection of the wave crest section and the wave trough section is a rounded transition.

9. The high-strength integrally formed retainer according to claim 1, characterized in that: The wave crest section is provided with an arc-shaped contact surface which contacts the arc-shaped surface of the cylindrical roller.

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