Tapered roller bearing and large-load tapered roller bearing

Abstract

The invention relates to the multifunctional technical field of low-speed large-load bearings and bearing outer rings. The large-load tapered roller bearing comprises a main shaft and a bearing assembly arranged on the peripheral side of the main shaft, the bearing assembly comprises a multifunctional bearing outer ring, a rolling body and a bearing inner ring, the rolling body is arranged between the bearing inner ring and the multifunctional bearing outer ring, and the rolling body makes contact with the inner side face of the multifunctional bearing outer ring. The bearing inner ring is arranged on the peripheral side of the main shaft, and the inner side face of the multifunctional bearing outer ring corresponds to the bearing inner ring to serve as a load mounting face. The multifunctional bearing outer ring and the outer load inner ring are designed into an integrated structure, so that the design mode that the bearing capacity can only be improved by adopting a higher-end bearing is solved, and the design requirement can be met by applying the bearing of the international first-line brand in a complex environment; the integrated design is superior to the international first-line brand in more complex environment application, and the integrated bearing can improve the bearing capacity and prolong the rolling life.

Description

Technical Field

[0001] The invention relates to the technical field of low-speed and high-load bearings, in particular to a tapered roller bearing and a high-load tapered roller bearing. Background Art

[0002] In the modern industrial field, especially in heavy machinery, large equipment and energy facilities, tapered roller bearings, as key transmission components, play a pivotal role. Its structural characteristics are that the outer ring and the inner ring are both tapered, the rolling element is a tapered roller, and the rolling element forms a point contact or line contact with the inner and outer rings, which can not only effectively disperse the radial force, but also withstand a large unidirectional axial force. Due to the existence of the contact angle, the large taper angle design enables the bearing to better adapt to the working environment dominated by axial loads. Tapered roller bearings are separable, that is, the inner ring assembly (including rollers and cages) and the outer ring can be installed independently, which is convenient for assembly and maintenance. These application environments are often accompanied by low speeds and extreme load conditions, which put extremely high demands on the bearing's load capacity, stability and durability. Traditional tapered roller bearing designs mostly follow the idea of ​​standardization and generalization, and their structural dimensions and material selections tend to adapt to a wide range of application scenarios rather than being optimized specifically for specific extreme working conditions.

[0003] Existing tapered roller bearings often reveal some limitations when facing low-speed, high-load working conditions. On the one hand, due to the general compatibility considered during design, the size ratio and wall thickness of the outer and inner rings of the bearing may not fully take into account the needs of such special working conditions, resulting in limited overall strength and radial and axial load-bearing capacity of the bearing. In particular, the difference between the inner and outer diameters of the bearing is small, and the minimum thickness of the inner and outer rings is insufficient, which directly affects the ability of the bearing to withstand extreme loads and limits its service life under heavy loads. On the other hand, if the design of the rolling element and the retainer is not precisely matched, such as an inappropriate pocket width or an excessively large roller arrangement gap, it will also increase friction losses during operation, affect bearing efficiency and accelerate wear.

[0004] In view of the above problems, existing solutions often cannot meet the industry's growing demand for low-speed, high-load bearings, especially in terms of ensuring long life and high reliability while also taking into account economy and ease of maintenance. Therefore, it is urgent to develop a new type of tapered roller bearing that can break through the limitations of traditional designs and significantly improve the bearing's load-bearing performance and service life through reasonable structural optimization and material selection, so as to better adapt to and meet the demanding requirements of modern heavy industry and special equipment fields. Summary of the invention

[0005] A series of simplified concepts are introduced in the Summary of the Invention, which will be further described in detail in the Detailed Description of the Invention. The Summary of the Invention does not mean to attempt to define the key features and essential technical features of the claimed technical solution, nor does it mean to attempt to determine the scope of protection of the claimed technical solution.

[0006] In view of the deficiencies in the prior art, the purpose of the present invention is to provide a tapered roller bearing and a high-load tapered roller bearing, which solves the problem of having to use imported high-end bearings to obtain higher load-bearing capacity by strengthening the inner and outer ring structures.

[0007] In order to achieve the above object, the present invention is implemented through the following technical solutions:

[0008] An embodiment of the present application provides a tapered roller bearing, comprising:

[0009] A multifunctional bearing outer ring including an inner rolling surface facing inward;

[0010] A rolling body, comprising a plurality of rollers and a retainer, wherein the rolling body is disposed between the inner ring of the bearing and the outer ring of the multifunctional bearing; the retainer is provided with a plurality of pockets corresponding to the number of the rollers, and the plurality of rollers are rotatably mounted in each of the pockets; and,

[0011] The inner ring of the bearing comprises an outer rolling surface located on the outer side surface, and the rolling body is rotatably arranged between the inner rolling surface and the outer rolling surface; wherein, the difference between the inner diameter of the inner ring of the bearing and the outer diameter of the outer ring of the multifunctional bearing is greater than the inner diameter of the inner ring of the bearing, and the maximum radial load of the tapered roller bearing is increased by more than 20%.

[0012] As a further implementation, the difference between the inner diameter of the bearing inner ring and the outer diameter of the multifunctional bearing outer ring is greater than 20% of the inner diameter of the bearing inner ring.

[0013] As a further implementation method, the minimum thickness of the bearing inner ring is at least 15% of the difference between the inner diameter of the bearing inner ring and the outer diameter of the multifunctional bearing outer ring, and the minimum thickness of the multifunctional bearing outer ring is at least 10% of the difference between the inner diameter of the bearing inner ring and the outer diameter of the multifunctional bearing outer ring.

[0014] As a further implementation method, the difference (UD) between the inner diameter of the bearing inner ring and the outer diameter of the multifunctional bearing outer ring is more than 1.7 times the inner diameter of the bearing inner ring.

[0015] In another aspect, the present application provides a low-speed, high-load tapered roller bearing, comprising:

[0016] A multifunctional bearing outer ring including an inner rolling surface facing inward;

[0017] A rolling body, comprising a plurality of rollers and a retainer, wherein the rolling body is disposed between the inner ring of the bearing and the outer ring of the multifunctional bearing; the retainer is provided with a plurality of pockets corresponding to the number of the rollers, and the plurality of rollers are rotatably mounted in each of the pockets; and,

[0018] The inner ring of the bearing comprises an outer rolling surface located on the outer side surface, the rolling body is rotatably arranged between the inner rolling surface and the outer rolling surface, the minimum width of the pocket is between 0.8 and 1.6 times the minimum radius of the roller, and the roller arrangement gap between two adjacent rollers is less than 2mm; the difference between the inner diameter of the inner ring of the bearing and the outer diameter of the outer ring of the multifunctional bearing is greater than the inner diameter of the inner ring of the bearing.

[0019] As a further implementation, the bearing inner ring has a minimum thickness of RD, the inner diameter of the bearing inner ring is ID, and the outer diameter of the multifunctional bearing outer ring is OD, wherein RD / (OD-ID)=X1, and X1 is between 0.10 and 0.15.

[0020] As a further implementation, the gap between the outer side surface of the retainer and the inner rolling surface of the outer ring of the multifunctional bearing is between 2-5 mm; or,

[0021] The gap between the outer side surface of the retainer and the inner rolling surface of the outer ring of the multifunctional bearing is between 5 / 9 and 1 / 3 of the minimum radius of the roller.

[0022] As a further implementation method, the bearing is a single-row bearing, and a group of rolling elements are arranged between an inner ring of the bearing and an outer ring of the multifunctional bearing; the width of the inner ring of the bearing is smaller than the width of the outer ring of the multifunctional bearing, and both axial end surfaces of the inner ring of the bearing are located a certain distance axially inward of the two axial end surfaces of the outer ring of the multifunctional bearing.

[0023] As a further implementation method, the bearing is a double-row bearing, and an integral multifunctional bearing outer ring has two bearing inner rings inside, the two bearing inner rings are separated by a spacer ring, and each of the two bearing inner rings is configured with a group of rolling elements, and the width of the two bearing inner rings plus the width of the spacer ring is smaller than the width of the multifunctional bearing outer ring; the radial load of the double-row bearing is K times the radial load of the single-row bearing, and K is greater than 1.5 and less than 2.

[0024] As a further implementation, the outer rolling surface of the inner ring of the bearing has a first cone angle, and the inner rolling surface of the outer ring of the multifunctional bearing has a second cone angle, and the second cone angle is greater than the first cone angle.

[0025] Compared with the prior art, the embodiments of the present invention have the following beneficial effects:

[0026] Enhanced load-bearing capacity: This technical solution directly solves the problem of limited bearing load capacity in the prior art by setting the inner diameter of the bearing inner ring to be greater than 100 mm and ensuring that the difference between the inner diameter of the bearing inner ring and the outer diameter of the outer ring exceeds the inner diameter of the inner ring, and increasing the radial load capacity to greater than 220,000 Newton meters. The large size difference design and enhanced load-bearing capacity enable the bearing to be more effectively applied to heavy-load environments, such as heavy machinery, mining equipment, etc., improving the stability and safety of the equipment.

[0027] Optimized structural design: The optimized dimensions of the inner and outer rings of the bearings, as well as the minimum thickness requirements of the inner and outer rings, not only enhance the structural strength of the bearings, but also extend their service life. This design overcomes the problem of early failure of traditional bearings due to insufficient thickness, and can significantly improve the durability and reliability of the bearings, especially under continuous heavy loads and impact loads.

[0028] On the other hand, the embodiment of the present application focuses on the application of large loads under low speed conditions. By setting the minimum width of the pocket to between 0.8 and 1.6 times the minimum radius of the roller and strictly controlling the roller arrangement gap between adjacent rollers to be less than 1 mm, the matching between the rolling element and the retainer is optimized, the vibration and noise during operation are reduced, and the stability of operation is improved. This fine design helps to maintain efficient and stable power transmission at low speeds and reduce energy loss.

[0029] Enhance the self-aligning ability of the bearing: It is proposed that there is a difference between the first cone angle of the outer rolling surface of the inner ring of the bearing and the second cone angle of the inner rolling surface of the outer ring of the multi-functional bearing, and the second cone angle is greater than the first cone angle. This design helps the bearing to automatically adjust the center during installation. Even if the axis has a slight offset, it can maintain a good contact state, reduce the additional stress caused by misalignment, and improve the adaptability and service life of the bearing.

[0030] In summary, compared with the existing technology, the technical solution in this patent significantly improves the load-bearing capacity, running smoothness, self-aligning performance and service life of tapered roller bearings under low speed and high load conditions by increasing the size difference, enhancing the structural strength, refining the rolling element design and adopting asymmetric taper angles. It solves the problems of small bearing load and short life in the existing technology and provides a more efficient and reliable solution for heavy industry and specific working conditions. BRIEF DESCRIPTION OF THE DRAWINGS

[0031] The accompanying drawings, which are incorporated in and constitute a part of this specification, illustrate embodiments consistent with the invention and, together with the description, serve to explain the principles of the invention.

[0032] In order to more clearly illustrate the embodiments of the present application or the technical solutions in the prior art, the drawings required for use in the embodiments or the description of the prior art will be briefly introduced below. Obviously, for ordinary technicians in this field, other drawings can be obtained based on these drawings without paying any creative labor.

[0033] Figure 1 It is a schematic diagram of the cross-sectional structure of a heavy-load tapered roller bearing in Embodiment 1 of the present invention.

[0034] Figure 2 It is a schematic diagram of the cross-sectional structure of the outer ring of the heavy-load tapered roller bearing in the first embodiment of the present invention.

[0035] Figure 3 It is a schematic diagram of the cross-sectional structure of the inner ring of the heavy-load tapered roller bearing in the first embodiment of the present invention.

[0036] Figure 4 It is a schematic diagram of the roller structure of a heavy-load tapered roller bearing in Embodiment 1 of the present invention.

[0037] Figure 5 It is a schematic diagram of the retainer structure of a heavy-load tapered roller bearing in Embodiment 1 of the present invention.

[0038] Figure 6 is along Figure 5 Schematic diagram of the cross-sectional structure at AA in the middle.

[0039] Figure 7 It is a schematic diagram of the cross-sectional structure of a heavy-load tapered roller bearing in Embodiment 2 of the present invention.

[0040] Figure 8 It is a schematic diagram of the cross-sectional structure of a heavy-load tapered roller bearing in Embodiment 3 of the present invention.

[0041] Fig. 9 It is a schematic diagram of the cross-sectional structure of the outer ring of the heavy-load tapered roller bearing in the third embodiment of the present invention.

[0042] Fig.10 It is a schematic diagram of the cross-sectional structure of a heavy-load tapered roller bearing in Embodiment 4 of the present invention.

[0043] In the figure: the distances or sizes between parts are exaggerated to show the positions of various parts, and the schematic diagram is for reference only.

[0044] Among them: bearing outer ring 2; transmission surface 20; inner rolling surface 21; roller 3; retainer 4; pocket hole 41; bearing inner ring 5; outer rolling surface 51; small rib 52; large rib 53; guide groove 54; spacer 6. DETAILED DESCRIPTION

[0045] In order to make the purpose, technical solutions and advantages of the embodiments of the present application clearer, the technical solutions in the embodiments of the present application will be clearly and completely described below in conjunction with the drawings in the embodiments of the present application. Obviously, the described embodiments are part of the embodiments of the present application, not all of the embodiments. Based on the embodiments in the present application, all other embodiments obtained by ordinary technicians in this field without making creative work belong to the scope of protection of this application. Therefore, the following detailed description of the embodiments of the present invention provided in the drawings is not intended to limit the scope of the invention claimed for protection, but merely represents the selected embodiments of the present invention. Based on the embodiments in the present invention, all other embodiments obtained by ordinary technicians in this field without making creative work belong to the scope of protection of the present invention.

[0046] It should be noted that the following detailed descriptions are illustrative and intended to provide further explanation of the present invention. Unless otherwise specified, all technical and scientific terms used in the present invention have the same meanings as those commonly understood by those skilled in the art to which the present invention belongs.

[0047] In order to solve the deficiencies in the prior art, an embodiment of the present application provides a low-speed, high-load bearing, which solves the problem of having to use imported high-end bearings to obtain a higher load-bearing capacity by strengthening the inner and outer ring structures.

[0048] like Figures 1 to 6 As shown, the embodiment of the present application provides a tapered roller bearing for low speed and high load, mainly comprising:

[0049] The multifunctional bearing outer ring 2 includes an inner rolling surface 21 facing inward, and the inner rolling surface 21 is an inner conical surface; the outer side surface of the multifunctional bearing outer ring 2 can be a mounting surface, which can be used to mount the inner mounting surface of the outer load setting, and its shape can be set according to assembly requirements and is not limited here.

[0050] A rolling body, comprising a plurality of rollers 3 and a retainer 4, wherein the rolling body is disposed between the inner ring of the bearing and the outer ring 2 of the multifunctional bearing; the retainer 4 is provided with a plurality of pockets 41 corresponding to the number of the rollers 3, and the plurality of rollers 3 are rotatably mounted in the pockets 41; and,

[0051] The bearing inner ring 5 includes an outer rolling surface 51 located on the outer side surface, and the outer rolling surface 51 is an outer conical surface. The rolling body is rotatably arranged between the inner rolling surface 21 and the outer rolling surface 51; wherein, the inner diameter ID of the bearing inner ring 5 is generally greater than 100 mm, and the difference UD between the inner diameter ID of the bearing inner ring 5 and the outer diameter OD of the multifunctional bearing outer ring 2 is greater than the inner diameter ID of the bearing inner ring 5, which can increase the maximum radial load of the tapered roller bearing by more than 20%, so as to increase the radial bearing capacity of the tapered roller 3 bearing to greater than 220,000 Newton meters.

[0052] Those skilled in the art will appreciate that the above-mentioned increase of the maximum load by more than 20% is compared with existing standard bearings with the same outer diameter.

[0053] Compared with the tapered roller bearings in the prior art, the embodiments of the present application have the following technical effects:

[0054] Enhanced load-bearing capacity: This technical solution sets the difference between the inner diameter of the inner ring and the outer diameter of the outer ring to exceed the inner diameter of the inner ring, and increases the radial load-bearing capacity to more than 220,000 Newton meters, which directly solves the problem of limited bearing load-bearing capacity in the prior art. The large size difference design and enhanced load-bearing capacity enable the bearing to be more effectively applied to heavy-load environments, such as heavy machinery, mining equipment, etc., and improve the stability and safety of the equipment.

[0055] Optimized structural design: The optimized dimensions of the inner and outer rings of the bearings, as well as the minimum thickness requirements of the inner and outer rings, not only enhance the structural strength of the bearings, but also extend their service life. This design overcomes the problem of early failure of traditional bearings due to insufficient strength, and can significantly improve the durability and reliability of the bearings, especially under continuous heavy loads and impact loads.

[0056] Material selection for the bearing components in this embodiment:

[0057] Bearing steel: Different grades of bearing steel can be selected, such as GCr15, SKF steel, etc., to meet different performance requirements.

[0058] Alloy materials: Use special alloy materials, such as stainless steel, high temperature resistant materials, etc. to adapt to special working environments.

[0059] In this embodiment, the bearing geometric dimensions vary, and the diameters of the inner and outer rings of the bearings are: although the inner diameter of the inner ring of the bearing is generally greater than 100 mm, the specific dimensions can be adjusted according to actual application requirements.

[0060] In this embodiment, the taper ratio of the inner rolling surface 21 and the outer rolling surface 51 of the bearing can also be varied to optimize the load-bearing capacity and axial positioning capability. Roller size: The diameter and length of the roller 3 can be adjusted according to the required load-bearing capacity and space constraints.

[0061] In the bearing retainer design of this embodiment, the retainer 4 can be made of different materials, such as brass, polyamide, etc., to adapt to different temperatures and lubrication conditions. The shape of the retainer 4 can be designed in different styles, such as window type, solid type, etc., to improve the distribution and movement characteristics of the roller 3.

[0062] The design of the tapered roller bearing not only solves the problems of traditional bearings in low-speed and high-load applications by adopting a special size ratio structure, but also significantly improves the bearing's load capacity and service life. This innovative design is of great significance to improving the overall performance and reliability of heavy machinery and equipment. In particular, considering its special size ratio relationship and high load capacity requirements, it shows that the design is not based on a simple combination of existing technologies, but is the result of in-depth research and innovative thinking on bearing structure and materials. Therefore, the design is non-obvious and represents an important technological advancement.

[0063] In this embodiment, the difference between the inner diameter of the bearing inner ring 5 and the outer diameter of the multifunctional bearing outer ring 2 is greater than 120 mm. For example, in this embodiment, the inner diameter ID of the bearing inner ring 5 is 127 mm, and the outer diameter OD of the multifunctional bearing outer ring 2 is 304.8 mm, so the difference UD is 177.8 mm, which is almost 1.4 times the spindle diameter. In this way, the strength and durability of the bearing inner ring 5 and the multifunctional bearing outer ring 2 can be closer to the parameters of the spindle. The outer side surface of the multifunctional bearing outer ring 2 can be a multifunctional assembly surface.

[0064] As a further implementation, the minimum thickness RD of the bearing inner ring 5 is about 12% of the difference UD between the inner diameter ID of the bearing inner ring 5 and the outer diameter OD of the multifunctional bearing outer ring 2, and the minimum thickness WD of the multifunctional bearing outer ring 2 is about 10% of the difference UD between the inner diameter ID of the bearing inner ring 5 and the outer diameter OD of the multifunctional bearing outer ring 2. Among them, the minimum thickness RD of the bearing inner ring 5 is greater than the minimum thickness WD of the multifunctional bearing outer ring 2, so as to ensure the life of the bearing inner ring 5 with heavier load; that is to say, the increased inner and outer diameter difference is basically allocated to enhance the strength of the bearing inner ring 5 and the bearing outer ring 2, and the enhancement of the inner ring is greater than that of the outer ring. By setting the minimum thickness ratio of the inner and outer rings of the bearing, the stability and strength of the bearing structure are ensured to prevent deformation or damage under high load.

[0065] Figure 2 1 is a schematic diagram of the cross-sectional structure of the outer ring of a low-speed, high-load tapered roller bearing in Embodiment 1 of the present invention. Figure 3 1 is a schematic diagram of the cross-sectional structure of the inner ring of a low-speed, high-load tapered roller bearing in Embodiment 1 of the present invention. Figure 4 Schematic diagram of the roller structure of a low-speed, high-load tapered roller bearing in Embodiment 1 of the present invention. Figure 5 1 is a schematic diagram of a retainer structure of a low-speed, high-load tapered roller bearing in a first embodiment of the present invention. Figure 6 is along Figure 5Schematic diagram of the cross-sectional structure at AA in the middle. In this embodiment, the gap between the outer side of the retainer 4 and the inner rolling surface 21 of the outer ring 2 of the multifunctional bearing is between 6-10mm; or the gap between the outer side of the retainer 4 and the inner rolling surface 21 of the outer ring 2 of the multifunctional bearing is between 5 / 9 and 1 / 3 of the minimum radius of the roller 3. In this way, the retainer 4 is moved outward so that the number of rollers can be further increased to more than 16. By accurately controlling the gap between the retainer and the outer ring, the gap between adjacent rollers can be reduced, thereby increasing the total number of rollers, optimizing the lubrication and thermal management of the bearing, and improving the operating efficiency and life of the bearing.

[0066] In this embodiment, the inner rolling surface 21 of the multifunctional bearing outer ring 2 is arranged close to one end of the multifunctional bearing outer ring 2, and the inner rolling surface 21 leaves a certain distance on the other end of the multifunctional bearing outer ring 2, and this distance is close to or greater than half the length of the roller 3, so as to leave enough sealing space.

[0067] In this embodiment, the inner ring 5 of the bearing includes a small rib 52, an outer rolling surface 51 and a large rib 53 located on the outer side surface, and guide grooves 54 are arranged between the outer rolling surface 51 and the small rib 52 and the large rib 53. The small rib 52 and the large rib 53 limit the roller 3 at both ends. The guide grooves 54, on the one hand, avoid affecting the rolling smoothness of the roller 3, and on the other hand, provide a supply channel for the lubricant to avoid lubrication failure between adjacent rollers 3.

[0068] As a further implementation, the radial bearing capacity of the tapered roller bearing is greater than 300,000 Newton meters, and the axial bearing capacity of the tapered roller 3 bearing is greater than 250,000 Newton meters. It is understood by those skilled in the art that the relationship between the axial bearing capacity and the radial bearing capacity of the tapered roller bearing mainly depends on the cone angle of the tapered roller 3 and the cone angles of the inner rolling surface and the outer rolling surface, thereby determining the two bearing capacities. Increasing the radial and axial bearing capacities to 300,000 Newton meters and 250,000 Newton meters, respectively, further expands the application range of the bearing under extreme working conditions.

[0069] As a further implementation, the bearing in this embodiment is a single-row bearing, and a group of rolling elements are arranged between one of the bearing inner rings 5 ​​and one of the multifunctional bearing outer rings 2; the width of the bearing inner ring 5 is smaller than the width of the multifunctional bearing outer ring 2, and both axial end faces of the bearing inner ring 5 are located at a certain distance inward of the axial end faces of the multifunctional bearing outer ring 2. In this way, both end faces of the bearing inner ring 5 are located on the inner side of the end face of the multifunctional bearing outer ring 2, so that after the end cover is arranged on the outer end face of the multifunctional bearing outer ring 2, sufficient lubrication space will be arranged for the rolling elements and the bearing inner ring 5, so as to retain more lubricating medium.

[0070] According to the following table, the tapered roller bearing of the first embodiment of the present application is compared with the tapered roller bearings of similar diameters from imported manufacturers for axial load C90 and radial load CA90. It can be found that the radial load of the tapered roller bearing of this embodiment can be 2-4 times that of similar imported products. This allows the bearing to be more effectively used in heavy-load environments, such as heavy machinery, mining equipment, etc., and improves the stability and safety of the equipment.

[0071] Table 1: Comparison between single-row bearings in Example 1 and existing products

[0072]

[0073] On the other hand, the embodiment of the present application Figure 7 As shown, the second embodiment of the present application provides a high-load tapered roller bearing 3, including:

[0074] Figure 7 It is a schematic diagram of the cross-sectional structure of the heavy-load tapered roller bearing in the second embodiment of the present invention. As shown in the figure, the main difference between it and the first embodiment is that two heavy-load tapered roller bearings in the first embodiment are installed back to back in a multifunctional bearing outer ring 2, wherein the two assembly parts assembled on both sides of the inner convex ring of the multifunctional bearing outer ring 2 can be regarded as the outer ring of the heavy-load tapered roller bearing in the first embodiment, and the outer side surface of the multifunctional bearing outer ring 2 in this embodiment can be the transmission surface 20, and the transmission surface 20 can be an assembly surface that is interference-fitted with the inner hole of other equipment, so as to facilitate the installation of external loads with this transmission surface.

[0075] On the other hand, the embodiment of the present application Figure 8 As shown, the third embodiment of the present application provides a high-load tapered roller bearing 3, including:

[0076] The multifunctional bearing outer ring 2 comprises an inner rolling surface 21 facing inward;

[0077] A rolling body, comprising a plurality of rollers 3 and a retainer 4, wherein the rolling body is disposed between the bearing inner ring 5 and the multifunctional bearing outer ring 2; the retainer 4 is provided with a plurality of pockets 41 corresponding to the number of the rollers 3, and the plurality of rollers 3 are rotatably mounted in each of the pockets 41; and,

[0078] The bearing inner ring 5 includes an outer rolling surface 51 located on the outer side surface, the rolling body is rotatably arranged between the inner rolling surface 21 and the outer rolling surface 51, the minimum width of the pocket 41 is between 0.8 and 1.6 times the minimum radius of the roller 3, and the roller arrangement gap between two adjacent rollers 3 is less than 2mm and greater than 0mm; the inner diameter ID of the bearing inner ring 5 is greater than 100mm, and the difference UD between the inner diameter ID of the bearing inner ring 5 and the outer diameter OD of the multifunctional bearing outer ring 2 is greater than the inner diameter ID of the bearing inner ring 5.

[0079] Roller Arrangement Clearance, the term used in this manual, refers to the radial clearance between the rolling surfaces of two adjacent rollers inside a roller bearing. By reducing this clearance, the number of rollers per unit length can be increased without affecting the normal rolling and lubrication of the rollers, thereby significantly improving the load capacity of the bearing. Reasonable control of the roller arrangement clearance can not only ensure the smooth operation of the bearing, but also effectively improve its load capacity and durability.

[0080] Material selection for the bearing components in this embodiment:

[0081] Bearing steel: Different grades of bearing steel can be selected, such as GCr15, SKF steel, etc., to meet different performance requirements.

[0082] Alloy materials: Use special alloy materials, such as stainless steel, high temperature resistant materials, etc. to adapt to special working environments.

[0083] The bearing geometry changes in this embodiment

[0084] Diameters of the inner and outer rings of the bearing: Although the inner diameter of the inner ring of the bearing must be greater than 100 mm, the specific size can be adjusted according to actual application requirements.

[0085] In this embodiment, the taper ratio of the inner rolling surface 21 and the outer rolling surface 51 of the bearing can also be varied to optimize the load-bearing capacity and axial positioning capability. Roller size: The diameter and length of the roller 3 can be adjusted according to the required load-bearing capacity and space constraints.

[0086] In the bearing retainer design of this embodiment, the retainer 4 can be made of different materials, such as brass, polyamide, etc., to adapt to different temperatures and lubrication conditions. The shape of the retainer 4 can be designed in different styles, such as window type, solid type, etc., to improve the distribution and movement characteristics of the roller 3.

[0087] The design of the tapered roller bearing not only solves the problems of traditional bearings in low-speed and high-load applications by adopting a special size ratio structure, but also significantly improves the bearing's load capacity and service life. This innovative design is of great significance to improving the overall performance and reliability of heavy machinery and equipment. In particular, considering its special size ratio relationship and high load capacity requirements, it shows that the design is not based on a simple combination of existing technologies, but is the result of in-depth research and innovative thinking on bearing structure and materials. Therefore, the design is non-obvious and represents an important technological advancement.

[0088] Fig. 9 It is a schematic diagram of the cross-sectional structure of the outer ring of the low-speed and high-load tapered roller bearing in Example 3 of the present invention. In this embodiment, the inner rolling surface 21 of the multifunctional bearing outer ring 2 is arranged close to the middle of the multifunctional bearing outer ring 2, and the inner rolling surface 21 leaves a certain distance on the outer end side of the multifunctional bearing outer ring 2, and this distance is close to or greater than half of the length of the roller 3, so as to leave enough sealing space.

[0089] It can be understood that the retainer and inner ring structure in the second embodiment of the present invention can refer to the first embodiment.

[0090] In this embodiment, the two bearing inner rings 5 ​​also include a small rib 52, an outer rolling surface 51 and a large rib 53 located on the outer side surface, and guide grooves 54 are arranged between the outer rolling surface 51 and the small rib 52 and the large rib 53. The small rib 52 and the large rib 53 limit the rollers 3 at both ends. The guide grooves 54, on the one hand, avoid affecting the rolling smoothness of the rollers 3, and on the other hand, provide a supply channel for the lubricant to avoid lubrication failure between adjacent rollers 3.

[0091] The bearing is a double-row bearing, and an integral multifunctional bearing outer ring 2 has two bearing inner rings 5 ​​inside, and the two bearing inner rings 5 ​​are separated by a spacer 6, and each of the two bearing inner rings 5 ​​is equipped with a set of rolling elements, and the width of the two bearing inner rings 5 ​​plus the width of the spacer 6 is less than the width of the multifunctional bearing outer ring 2; the radial load of the double-row bearing is K times the radial load of the single-row bearing, and K is greater than 1.5 and less than 2. The design of the double-row bearing significantly improves the bearing's load-bearing capacity by increasing the number of inner rings and rolling elements, while maintaining a compact size.

[0092] As a further implementation, the bearing inner ring 5 has a minimum thickness of RD, the inner diameter of the bearing inner ring 5 is ID, and the outer diameter of the multifunctional bearing outer ring 2 is OD, wherein RD / (OD-ID)=X1, X1 is between 0.10 and 0.15. In this way, it is convenient to implement the product idea of ​​this embodiment in the design, and by setting the ratio of the inner ring thickness to the difference between the inner and outer ring diameters, a flexible design method is provided, which can adjust the size and load capacity of the bearing according to different application requirements.

[0093] As a further implementation, the gap between the outer side of the retainer 4 and the inner rolling surface 21 of the outer ring 2 of the multifunctional bearing is between 6-10 mm; or the gap between the outer side of the retainer 4 and the inner rolling surface 21 of the outer ring 2 of the multifunctional bearing is between 5 / 9 and 1 / 3 of the minimum radius of the roller 3. By precisely controlling the gap between the retainer and the outer ring, the gap between adjacent rollers can be reduced, thereby increasing the total number of rollers, optimizing the lubrication and thermal management of the bearing, and improving the operating efficiency and life of the bearing.

[0094] As a further implementation, the outer rolling surface 51 of the bearing inner ring 5 has a first cone angle, and the inner rolling surface 21 of the multifunctional bearing outer ring 2 has a second cone angle, and the second cone angle is greater than the first cone angle. By adjusting the cone angles of the inner and outer rings, the rolling contact of the bearing can be optimized, friction and wear can be reduced, and the service life of the bearing can be extended.

[0095] Table 2: Comparison of double row bearings in embodiments 2, 3 and 4 with existing products

[0096]

[0097]

[0098] Compared with the prior art, the embodiments of the present invention have the following beneficial effects:

[0099] Enhanced load-bearing capacity: This technical solution sets the inner diameter ID of the inner ring 5 of the bearing to be greater than 100mm, and ensures that the difference UD between the inner diameter ID of the inner ring 5 of the bearing and the outer diameter of the outer ring not only exceeds the inner diameter of the inner ring, but also increases the radial load-bearing capacity to greater than 220,000 Newton meters, which directly solves the problem of limited bearing load-bearing capacity in the prior art. The large size difference design and enhanced load-bearing capacity enable the bearing to be more effectively applied to heavy-load environments, such as heavy machinery, mining equipment, etc., and improve the stability and safety of the equipment.

[0100] Optimized structural design: The optimized dimensions of the inner and outer rings of the bearings, as well as the minimum thickness requirements of the inner and outer rings, not only enhance the structural strength of the bearings, but also extend their service life. This design overcomes the problem of early failure of traditional bearings due to insufficient thickness, and can significantly improve the durability and reliability of the bearings, especially under continuous heavy loads and impact loads.

[0101] The embodiment of the present application focuses on the application of large loads under low speed conditions. By setting the minimum width of the pocket 41 to between 0.8 and 1.6 times the minimum radius of the roller 3 and strictly controlling the roller arrangement gap between adjacent rollers 3 to be less than 1 mm, the matching between the rolling element and the retainer 4 is optimized, the vibration and noise during operation are reduced, and the stability of operation is improved. This fine design helps to maintain efficient and stable power transmission at low speeds and reduce energy loss.

[0102] Enhance the self-aligning ability of the bearing: It is proposed that there is a difference between the first cone angle of the outer rolling surface 51 of the bearing inner ring 5 and the second cone angle of the inner rolling surface 21 of the multifunctional bearing outer ring 2, and the second cone angle is greater than the first cone angle. This design helps the bearing to automatically adjust the center during installation, and even if the axis has a slight offset, it can maintain a good contact state, reduce the additional stress caused by misalignment, and improve the adaptability and service life of the bearing.

[0103] Fig.10 This is a schematic diagram of the cross-sectional structure of a high-load tapered roller bearing in the fourth embodiment of the present invention. As shown in the figure, the main difference between the fourth embodiment and the second embodiment is that the outer side surface of the multifunctional bearing outer ring 2 can be a transmission surface 20, and the transmission surface 20 includes a plurality of belt grooves arranged along the axial direction, so as to be used to load a plurality of transmission belts, or to assemble a transmission belt with a plurality of convex teeth on the inner side. In this way, the multifunctional bearing outer ring 2 is integrated with the outer transmission surface, thereby reducing the number of parts and improving the integration degree of assembly.

[0104] In summary, compared with the existing technology, the technical solution in this patent significantly improves the load-bearing capacity, running smoothness, self-aligning performance and service life of tapered roller bearings under low speed and high load conditions by increasing the size difference, enhancing the structural strength, refining the rolling element design and adopting asymmetric taper angles. It solves the problems of small bearing load and short life in the existing technology and provides a more efficient and reliable solution for heavy industry and specific working conditions.

[0105] It should be noted that, in this article, relational terms such as "first" and "second" are only used to distinguish one entity or operation from another entity or operation, and do not necessarily require or imply any such actual relationship or order between these entities or operations. Moreover, the terms "include", "comprise" or any other variants thereof are intended to cover non-exclusive inclusion, so that a process, method, article or device including a series of elements includes not only those elements, but also other elements not explicitly listed, or also includes elements inherent to such process, method, article or device. In the absence of further restrictions, the elements defined by the sentence "comprise a ..." do not exclude the existence of other identical elements in the process, method, article or device including the elements.

[0106] The above description is only a specific embodiment of the present invention, so that those skilled in the art can understand or implement the present invention. Various modifications to these embodiments will be apparent to those skilled in the art, and the general principles defined herein can be implemented in other embodiments without departing from the general inventive concept of the present invention. Therefore, the present invention will not be limited to the embodiments shown herein, but should conform to the widest scope consistent with the principles and novel features applied herein.

Claims

1. A tapered roller bearing, characterized in that: include A multifunctional bearing outer ring including an inner rolling surface facing inward; A rolling body, comprising a plurality of rollers and a retainer, wherein the rolling body is arranged between the inner ring of the bearing and the outer ring of the multifunctional bearing; the retainer is provided with a plurality of pockets corresponding to the number of the rollers, and the plurality of rollers are rotatably mounted in each of the pockets; and, The inner ring of the bearing comprises an outer rolling surface located on the outer side surface, and the rolling body is rotatably arranged between the inner rolling surface and the outer rolling surface; wherein the difference (UD) between the inner diameter of the inner ring of the bearing and the outer diameter of the outer ring of the multifunctional bearing is greater than the inner diameter (ID) of the inner ring of the bearing, and the maximum radial load of the tapered roller bearing is increased by more than 20%.

2. The tapered roller bearing according to claim 1, characterized in that: The difference between the inner diameter of the bearing inner ring and the outer diameter of the multifunctional bearing outer ring is greater than 20% of the inner diameter of the bearing inner ring.

3. The tapered roller bearing according to claim 1, characterized in that: The minimum thickness (RD) of the bearing inner ring is about 12% of the difference between the inner diameter of the bearing inner ring and the outer diameter of the multifunctional bearing outer ring, and the minimum thickness (WD) of the multifunctional bearing outer ring is about 10% of the difference between the inner diameter of the bearing inner ring and the outer diameter of the multifunctional bearing outer ring.

4. The tapered roller bearing according to any one of claims 1 to 3, characterized in that: The difference (UD) between the inner diameter of the bearing inner ring and the outer diameter of the multifunctional bearing outer ring is more than 1.7 times the inner diameter of the bearing inner ring.

5. The tapered roller bearing according to claim 1, characterized in that: The bearing is a single-row bearing or a double-row bearing.

6. A high-load tapered roller bearing, characterized in that: include A multifunctional bearing outer ring including an inner rolling surface facing inward; A rolling body, comprising a plurality of rollers and a retainer, wherein the rolling body is arranged between the inner ring of the bearing and the outer ring of the multifunctional bearing; the retainer is provided with a plurality of pockets corresponding to the number of the rollers, and the plurality of rollers are rotatably mounted in each of the pockets; and, The inner ring of the bearing comprises an outer rolling surface located on the outer side surface, the rolling body is rotatably arranged between the inner rolling surface and the outer rolling surface, the minimum width of the pocket is between 0.8 and 1.6 times the minimum radius of the roller, and the roller arrangement gap between two adjacent rollers is less than 2mm; the difference between the inner diameter of the inner ring of the bearing and the outer diameter of the outer ring of the multifunctional bearing is greater than the inner diameter of the inner ring of the bearing.

7. The high load tapered roller bearing according to claim 6, characterized in that: The bearing inner ring has a minimum thickness of RD, the inner diameter of the bearing inner ring is ID, and the outer diameter of the multifunctional bearing outer ring is OD, wherein RD / (OD-ID)=X1, and X1 is between 0.10 and 0.

15.

8. The high load tapered roller bearing according to claim 6, characterized in that: The clearance between the outer side surface of the retainer and the inner rolling surface of the outer ring of the multifunctional bearing is between 6-10 mm; or The gap between the outer side surface of the retainer and the inner rolling surface of the outer ring of the multifunctional bearing is between 5 / 9 and 1 / 3 of the minimum radius of the roller.

9. The high load tapered roller bearing according to claim 6, characterized in that: The bearing is a single-row bearing, and a group of rolling elements are arranged between an inner ring of the bearing and an outer ring of the multifunctional bearing; the width of the inner ring of the bearing is smaller than the width of the outer ring of the multifunctional bearing.

10. The high load tapered roller bearing according to claim 6, characterized in that: The bearing is a double-row bearing, and an integral multifunctional bearing outer ring has two bearing inner rings inside, the two bearing inner rings are separated by a spacer ring, each of the two bearing inner rings is configured with a group of rolling elements, and the width of the two bearing inner rings plus the width of the spacer ring is smaller than the width of the multifunctional bearing outer ring; the radial load of the double-row bearing is K times the radial load of the single-row bearing, and K is greater than 1.5 and less than 2.

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