Outer-ring-free cylindrical roller bearing structure for wind turbine gearbox

Abstract

The present disclosure relates to an outer-ring-free cylindrical roller bearing structure for a wind turbine gearbox, comprising: an inner ring, a first raceway and a second raceway being provided on the periphery of the inner ring; a first rolling body and a second rolling body, which are respectively located in the first raceway and the second raceway; and a first retainer and a second retainer, which are respectively used for circumferentially separating the first rolling body in the first raceway and the second rolling body in the second raceway, wherein the inner diameter of the first retainer is less than the diameter of a circle where the center of the first rolling body is located, the inner diameter of the second retainer is greater than the diameter of a circle where the center of the second rolling body is located, and the first retainer and the second retainer partially overlap in the axial direction. The two retainers axially overlap, and under the same axial dimension condition, such retainers can increase the lengths of the rolling bodies to the maximum extent, thereby maximizing the static bearing capacity of the bearing, so that a planetary gearbox achieves larger power density.

Description

Cylindrical roller bearing structure without outer ring for wind turbine gearbox Technical Field

[0001] The present invention relates to the technical field of bearings, and in particular to a cylindrical roller bearing structure without an outer ring for a wind power gearbox. Background Art

[0002] A wind turbine, also known as a windmill, is an electrical device that converts wind energy into mechanical energy and then mechanical energy into electrical energy. A wind turbine typically consists of a rotor, planetary gearbox, and generator. The rotor converts the kinetic energy of the air into rotational mechanical energy, while the gearbox converts the high-torque, low-speed mechanical energy generated by the rotor into the low-torque, high-speed mechanical energy required by the generator.

[0003] In the planetary gearbox in the wind turbine (referred to as wind turbine gearbox), a cylindrical roller bearing structure without an outer ring is often provided to provide relative rotation and radial support for the planetary gears in the planetary gearbox. Since the planetary gearbox is usually subjected to the force of the wind wheel and the force during gear transmission, the radial load-bearing capacity of the cylindrical roller bearing structure without an outer ring is required to be relatively high.

[0004] Summary of the Invention

[0005] In order to overcome the problems existing in the related art, the present disclosure provides a cylindrical roller bearing structure without an outer ring for a wind power gearbox.

[0006] According to a first aspect of an embodiment of the present disclosure, the present disclosure provides a cylindrical roller bearing structure without an outer ring for a wind power gearbox, comprising: an inner ring, a first row of raceways and a second row of raceways being provided on the outer periphery of the inner ring; a first rolling body and a second rolling body, respectively located in the first row of raceways and the second row of raceways; and a first retaining frame and a second retaining frame, respectively used to circumferentially separate the first rolling body of the first row of raceways and the second rolling body of the second row of raceways, wherein the outer diameter of the first retaining frame is smaller than the diameter of the circle on which the center of the first rolling body is located, the inner diameter of the second retaining frame is larger than the diameter of the circle on which the center of the second rolling body is located, and the first retaining frame and the second retaining frame partially overlap in the axial direction.

[0007] In some embodiments, the diameter of the first rolling body is equal to the diameter of the second rolling body; and the axial length of the first rolling body is equal to or different from the axial length of the second rolling body.

[0008] In some embodiments, the outer periphery of the inner ring further includes an intermediate rib, which protrudes radially from the outer periphery of the inner ring, and the first row of raceways and the second row of raceways share the intermediate rib, wherein the intermediate rib overlaps with the first retaining frame and the second retaining frame in the axial direction, and the axial width of the intermediate rib satisfies: BS1≥X1+μ or BS1≥X2+μ, X1 and X2 are the axial overlapping lengths of the first retaining frame and the second retaining frame with the intermediate rib, respectively, and μ is the axial movement amount of the first retaining frame and the second retaining frame.

[0009] In some embodiments, the intermediate rib is integrally formed with the inner ring.

[0010] In some embodiments, the first retaining frame and the second retaining frame are spaced apart in the radial direction, and the spacing distance e satisfies: 0≤e≤0.1Dw1 or 0≤e≤0.1Dw2, where Dw1 and Dw2 are the diameters of the first rolling element and the second rolling element, respectively.

[0011] In some embodiments, a thickness of the first retainer is equal to a thickness of the second retainer.

[0012] In some embodiments, the outer ringless cylindrical roller bearing structure also includes: a fixed rib, which is located at one axial end of the inner ring, forms a first row of raceways with the intermediate rib, and is used to abut against the first rolling body; a movable rib, which is located at the other axial end of the inner ring, forms a second row of raceways with the intermediate rib, and is used to abut against the second rolling body.

[0013] In some embodiments, the fixed rib is integrally formed with the inner ring; and the movable retaining ring is detachably connected to the inner ring by interference fit, clamping ring connection or fasteners.

[0014] In some embodiments, when the two cylindrical roller bearing structures without outer rings are arranged side by side in the axial direction, the two first rolling elements of the two cylindrical roller bearing structures without outer rings are adjacent, or the two second rolling elements of the two cylindrical roller bearing structures without outer rings are adjacent.

[0015] In some embodiments, the second cage is guided by the second rolling elements; or the second cage is guided by the outer ring.

[0016] The technical solution provided by the embodiments of the present disclosure can achieve the following beneficial effects: two rows of cages—one row of inner ring-guided first cages and the other row of non-inner ring-guided second cages—partially overlap axially, fully utilizing the axial space at the center rib of the double-row bearing. Given the same axial dimensions, this cage arrangement maximizes the rolling element length, thereby maximizing the static load capacity of the bearing and achieving higher power density for the planetary gearbox. BRIEF DESCRIPTION OF THE DRAWINGS

[0017] The accompanying drawings, which are incorporated in and constitute a part of this specification, illustrate embodiments consistent with the present disclosure and, together with the description, serve to explain the principles of the present disclosure.

[0018] FIG1 is a longitudinal sectional view of a cylindrical roller bearing structure without an outer ring in the related art;

[0019] FIG2 is a front view of a cylindrical roller bearing structure without an outer ring having two rows of raceways according to an exemplary embodiment;

[0020] FIG3 is a front view of two first rolling elements of the outer ringless cylindrical roller bearing structure in FIG2 when they are arranged adjacent to each other;

[0021] FIG4 is a front view of two second rolling elements of the outer ringless cylindrical roller bearing structure in FIG2 when they are arranged adjacent to each other;

[0022] FIG5 is a schematic diagram showing the dimensional relationship of the cylindrical roller bearing structure without an outer ring shown in FIG4 . DETAILED DESCRIPTION

[0023] Exemplary embodiments will be described in detail herein, with examples illustrated in the accompanying drawings. In the following description, when referring to the drawings, identical numerals in different figures represent identical or similar elements, unless otherwise indicated. The embodiments described in the following exemplary embodiments are not intended to represent all possible embodiments consistent with the present disclosure. Rather, they are merely examples of apparatus and methods consistent with certain aspects of the present disclosure, as detailed in the appended claims.

[0024] In the present invention, unless otherwise specified, the axial direction A, radial direction R, and circumferential direction refer to the axial direction A, radial direction R, and circumferential direction, respectively, of a cylindrical roller bearing structure without an outer ring. One axial end refers to the left side as shown in Figure 2, and the other axial end refers to the right side as shown in Figure 2. The radially outer side refers to the side in the radial direction R that is farther from the center axis O in Figures 2 to 4, and the radially inner side refers to the side in the radial direction R that is closer to the center axis O in Figures 2 to 4.

[0025] The outer ringless cylindrical roller bearing structure 100 is suitable for installation in a planetary gearbox for a wind turbine. Within the limited axial space of a planetary gearbox, the length of the rolling element 20 used directly determines the static load capacity of the bearing. The longer the axial length of the rolling element, the higher the static load capacity of the bearing.

[0026] The current solution uses two symmetrically arranged double-row bearings. For example, the four-row bearing in Figure 1 features a retainer 30 guided by the inner ring 10. As the torque density of user planetary gearboxes increases, the requirements for the static load capacity of bearings are also increasing. A disadvantage of double-row bearings in related art is the poor utilization of the axial and radial space at the intermediate rib 11, which limits the length of the rolling elements 20 and results in a relatively low static load capacity. The bearing pitch circle refers to the circle where the center of the rolling element 20 lies relative to the central axis of the inner ring.

[0027] To solve the above technical problems, the present disclosure provides a cylindrical roller bearing structure 100 without an outer ring for a wind power gearbox. As shown in FIG. 2 to FIG. 5 , the cylindrical roller bearing structure 100 without an outer ring includes an inner ring 10 , rolling elements 20 and a retaining frame 30 .

[0028] Specifically, the outer circumference of the inner ring 10 is provided with an intermediate rib 11, a first row of raceways 12, and a second row of raceways 13. The first row of raceways 12 and the second row of raceways 13 are arranged on the outer circumference of the inner ring 10 along the axial direction A. The intermediate rib 11 protrudes from the outer circumference of the inner ring 10 in the radial direction R and is located between the first row of raceways 12 and the second row of raceways 13 in the axial direction A. Therefore, the first row of raceways 12 and the second row of raceways 13 share the intermediate rib 11.

[0029] The rolling elements include first rolling elements 21 and second rolling elements 22. The first rolling elements 21 are located in the first row of raceways 12, and the second rolling elements 22 are located in the second row of raceways 13. The retainers include first retainers 31 and second retainers 32. The first retainer 31 is used to guide and circumferentially separate the first rolling elements 21 located in the first row of raceways 12, and the second retainer 32 is used to guide and circumferentially separate the second rolling elements 22 located in the second row of raceways 13.

[0030] Furthermore, the outer diameter of the first retainer 31 is smaller than the diameter of the circle where the center of the first rolling element 21 is located, the inner diameter of the second retainer 32 is larger than the diameter of the circle where the center of the second rolling element 22 is located, and the first retainer 31 and the second retainer 32 partially overlap in the axial direction A.

[0031] As can be seen, the first retainer 31 is located below the pitch circle of the bearing where the first rolling element 21 resides. The first retainer 31 is guided by the inner ring 10 and corrects the movement of the first rolling element 21 by colliding with the inner ring 10. The second retainer 32 is located above the pitch circle of the bearing where the second rolling element 22 resides. The second retainer 32 can be guided by the second rolling element 22 or by the outer ring, without specific limitation.

[0032] In addition, the outer wall of the first retaining frame 31 is located below the pitch circle of the bearing where the first rolling element 21 is located, and the inner wall of the second retaining frame 32 is located above the pitch circle of the bearing where the second rolling element 22 is located. Therefore, the first retaining frame 31 and the second retaining frame 32 can also make full use of the space on the radial direction R of the intermediate rib 11, so that the adjacent ends of the first retaining frame 31 and the second retaining frame 32 can partially overlap in the axial direction A.

[0033] Since the two rows of retainers partially overlap in the axial direction A, the axial space at the middle rib 11 of the double-row bearing can be fully utilized while the axial length of the double-row bearing remains unchanged. Therefore, the axial length of the middle rib 11 can be reduced, thereby increasing the sum of the axial lengths of the first rolling element 21 and the second rolling element 22.

[0034] The arrangement of the retainer of the outer ringless cylindrical roller bearing structure 100 disclosed in the present invention can maximize the axial length of the first rolling element 21 and / or the second rolling element 22, thereby maximizing the overall static load-bearing capacity of the outer ringless cylindrical roller bearing structure 100 and enabling the planetary gearbox to obtain a higher power density.

[0035] 5 , the diameter Dw1 of the first rolling element 21 is equal to the diameter Dw2 of the second rolling element 22. Furthermore, in some embodiments, the axial length Lw1 of the first rolling element 21 is equal to or different from the axial length Lw2 of the second rolling element 22.

[0036] The first retainer 31 and the second retainer 32 partially overlap in the axial direction A, thereby reducing the space occupied by the intermediate rib 11 in the axial direction A. When the axial length of the cylindrical roller bearing structure 100 without an outer ring remains unchanged, in the embodiments shown in Figures 2 to 5, the reduced axial length of the intermediate rib 11 can be compensated to the pocket of the second retainer 32, which is equivalent to increasing the axial length of the pocket of the second retainer 32, so that the axial length Lw2 of the second rolling element 22 is also increased accordingly. Therefore, the axial length Lw1 of the first rolling element 21 remains unchanged and is less than the axial length Lw2 of the second rolling element 22.

[0037] Similarly, in some other embodiments, the axial length of the pocket of the second retaining frame 32 can be kept unchanged, and the reduced axial length of the intermediate rib 11 can be compensated by the pocket of the first retaining frame 31, thereby increasing the axial length of the pocket of the first retaining frame 31 and correspondingly increasing the axial length Lw1 of the first rolling element 21.

[0038] In other embodiments, the reduced axial length of the intermediate rib 11 can be evenly compensated to the axial length of the pocket of the first retaining frame 31 and the axial length of the pocket of the second retaining frame 32, so that the axial length of the first rolling body 21 is equal to the axial length Lw2 of the second rolling body 22.

[0039] In some embodiments, the middle rib 11 overlaps with the first retaining frame 31 and the second retaining frame 32 in the axial direction A, and the axial A width of the middle rib 11 satisfies: BS1≥X1+μ or BS1≥X2+μ, X1 and X2 are the axial A overlapping lengths of the first retaining frame 31 and the second retaining frame 32 with the middle rib 11, respectively, and μ is the axial A movement amount of the first retaining frame 31 or the second retaining frame 32.

[0040] In the related art, as shown in FIG1 , the intermediate rib 11 also overlaps the first retainer 31 and the second retainer 32 in the axial direction A. However, the axial width A of the intermediate rib 11 is BS1 = X1 + μ + X2 + μ = X1 + X2 + 2μ. X1 and X2 can be equal, so BS1 = 2X1 + 2μ = 2X2 + 2μ = 2(X1 + μ) = 2(X2 + μ).

[0041] Compared with the related art, under the same axial dimension conditions, the structural arrangement of the first retaining frame 31 and the second retaining frame 32 disclosed in the present invention can save the axial length of the intermediate rib 11 by at least X1+μ or X2+μ, so that the axial length of the first rolling element 21 and / or the second rolling element 22 can be increased by at least X1+μ or X2+μ, thereby maximizing the overall static load-bearing capacity of the outer ringless cylindrical roller bearing structure 100 and enabling the planetary gearbox to obtain a higher power density.

[0042] In some embodiments, the intermediate rib 11 is integrally formed with the inner ring 10. The integrally formed inner ring 10 and intermediate rib 11 fix the axial position A of the intermediate rib 11, increases the strength of the inner ring 10 or the intermediate rib 11, and reduces the number of parts.

[0043] In other embodiments, the intermediate rib 11 can also be formed separately from the inner ring 10. The intermediate rib 11 is sleeved on the outer circumference of the inner ring 10 through an interference fit, or a rib groove is provided on the outer circumference of the inner ring 10, and the intermediate rib 11 is snapped into the rib groove. The separately formed intermediate rib 11 can be adjusted in position on the inner ring 10 to adjust the axial length of the first row of raceways 12 or the second row of raceways 13, thereby accommodating first rolling elements 21 or second rolling elements 22 of different axial lengths, thereby increasing the adaptability of the outer ringless cylindrical roller bearing structure 100.

[0044] Furthermore, as can be seen from the above, the outer wall of the first retainer 31 is located below the pitch circle of the bearing in which the first rolling element 21 is located, while the inner wall of the second retainer 32 is located above the pitch circle of the bearing in which the second rolling element 22 is located. Therefore, the first retainer 31 and the second retainer 32 do not overlap in the radial direction R. That is, the outer wall of the first retainer 31 and the inner wall of the second retainer 32 can be in contact with each other or spaced apart in the radial direction R. In this embodiment, as shown in Figures 2 to 5, the first retainer 31 and the second retainer 32 can be spaced apart in the radial direction R. The first retainer 31 and the second retainer 32 spaced apart in the radial direction R prevent collision during the correction of the operation of the first rolling element 21 and the second rolling element 22.

[0045] Furthermore, the spacing e between the first retainer 31 and the second retainer 32 in the radial direction R can satisfy the following conditions: 0 ≤ e ≤ 0.1Dw1 or 0 ≤ e ≤ 0.1Dw2, where Dw1 and Dw2 are the diameters of the first rolling element 21 and the second rolling element 22, respectively. Therefore, a smaller spacing e between the first retainer 31 and the second retainer 32 reduces the diameter of the second retainer 32, lowering costs and reducing the space occupied by the second retainer 32 in the radial direction R.

[0046] In some embodiments, the thickness S1 of the first retainer 31 is equal to the thickness S2 of the second retainer 32, i.e., S1 = S2. The first retainer 31 and the second retainer 32 can be made of steel and can be stamped from the same steel billet, thereby improving steel billet utilization, reducing steel billet waste, and lowering production costs.

[0047] In this embodiment, as shown in Figure 5, the thickness of the intermediate rib 11 is H≤0.25Dw1 or H≤0.25Dw2, and the thickness of the first retaining frame 31 and the second retaining frame 32 is S1=S2≤0.2Dw1 or S1=S2≤0.2Dw2. Therefore, the sum of the thickness H of the intermediate rib 11 and the thickness S1 of the first retaining frame 31 is H+S1≤0.45Dw1 or H+S1≤0.45Dw2, so that the outer wall of the first retaining frame 31 can be located below the pitch circle of the bearing where the first rolling element 21 is located.

[0048] In some embodiments, the outer ringless cylindrical roller bearing structure 100 further includes a fixed rib 14 and a movable retaining ring 40. The fixed rib 14 is located at one axial end of the inner ring 10. The fixed rib 14 and the intermediate rib 11 form a first row of raceways 12 for contacting the first rolling elements 21. The movable retaining ring 40 is located at the other axial end of the inner ring 10. The fixed rib 14 and the intermediate rib 11 form a second row of raceways 13 for contacting the second rolling elements 22.

[0049] In the present disclosure, since the first retaining frame 31 and the second retaining frame 32 at least partially overlap in the axial direction A, it is necessary to install the first retaining frame 31 and the first rolling element 21 first, and then install the second retaining frame 32 and the second rolling element 22. Providing a movable retaining ring 40 at the other axial end of the inner ring 10 is conducive to achieving the above-mentioned installation sequence. In addition, the movable single ring can also axially limit the axial position of the second rolling element 22.

[0050] Furthermore, the first retaining frame 31 is located below the pitch circle of the bearing where the first rolling element 21 is located. Therefore, the first retaining frame 31 does not have the function of retaining the first rolling element 21 in the radial direction R. When the outer ringless cylindrical roller bearing structure 100 disclosed in the present invention is assembled inside the factory, the first retaining frame 31 is first installed into the inner ring 10, and then a rubber band is put on the first retaining frame 31, and then the first rolling element 21 is placed into the pocket from the radial outside of the first retaining frame 31. In order to avoid the first rolling element 21 from scattering during assembly and transportation, the first rolling element 21 needs to be assisted by cable ties and rubber bands to retain it in the pocket of the first retaining frame 31.

[0051] After assembling the first retaining frame 31 and the first rolling element 21, assemble the second retaining frame 32 and the second rolling element 22, and insert the second rolling element 22 into the pocket of the second retaining frame 32 from the radial inner side of the second retaining frame 32. The circumferential size of the pocket is smaller than the diameter Dw2 of the second rolling element 22, so that the second rolling element 22 will not fall out of the pocket of the second rolling element 22 in the radial direction R. Therefore, the second retaining frame 32 has a retaining function for the second rolling element 22 in the radial direction R.

[0052] Furthermore, an inner envelope circle is formed on the radial inner side of the second rolling element 22, and then the other axial end of the inner ring 10 is inserted into the inner envelope circle, and then the movable retaining ring 40 is installed to the other axial end of the inner ring 10 for abutting against the end face of the second rolling element 22, so that the inner ring 10, the second retaining frame 32 and the second rolling element 22 are in an inseparable state.

[0053] Compared with the double-row bearing structure in the related art, the outer ringless cylindrical roller bearing structure 100 with double-row raceways disclosed in the present invention does not require the assistance of rubber bands during assembly and transportation of at least the second rolling element 22 and the second retaining frame 32, and there is no risk of the second rolling element 22 being scattered during the customer's installation, which is conducive to assembly, transportation, installation and disassembly, and the bearing has high safety.

[0054] In some embodiments, the fixed rib 14 is integrally formed with the inner ring 10. The fixed rib 14 and the intermediate rib 11 of the first row of raceways 12 have equal thickness H. This allows both ends of the first retainer 31 to contact the inner ring 10 when correcting the operation of the first rolling element 21, forming the first retainer 31 guided by the inner ring 10. Furthermore, both the fixed rib 14 and the intermediate rib 11 can be integrally formed with the inner ring 10. This integral structure makes the inner ring 10 more stable, reduces the number of parts, and facilitates processing and transportation.

[0055] Furthermore, the movable retaining ring 40 is detachably connected to the inner ring 10 by interference fit, clamping ring connection or fasteners. The movable retaining ring 40 is detachably connected to the inner ring 10 to facilitate the installation of the second retaining frame 32 and the second rolling element 22.

[0056] In some embodiments, when two outer ringless cylindrical roller bearing structures 100 are arranged side by side along the axial direction A, the two outer ringless cylindrical roller bearing structures 100 constitute a bearing structure having four raceway rows. As shown in FIG3 , two second retainers 32 located above the bearing pitch circle may be adjacent, i.e., the two second retainers 32 located above the bearing pitch circle are located between two first retainers 31 located below the bearing pitch circle along the axial direction A. As shown in FIG4 , two first retainers 31 located below the bearing pitch circle may be adjacent, i.e., the two first retainers 31 located below the bearing pitch circle are located between two second retainers 32 located above the bearing pitch circle along the axial direction A.

[0057] In addition, in some embodiments, a first retainer 31 located below the bearing pitch circle in a cylindrical roller bearing structure 100 without an outer ring may be adjacent to a second retainer 32 located above the bearing pitch circle in another cylindrical roller bearing structure 100 without an outer ring, thereby forming an arrangement in which the first retainer 31 located below the bearing pitch circle and the second retainer 32 located above the bearing pitch circle are staggered in the axial direction A.

[0058] Figures 3 and 4 are merely exemplary examples of the arrangement of two cylindrical roller bearing structures 100 without outer rings arranged side by side along the axial direction A. In some other embodiments, more than two cylindrical roller bearing structures 100 without outer rings can be arranged side by side along the axial direction A, for example, three or four, etc., according to design requirements, such as the load-bearing capacity of the bearing structure. This is not specifically limited here.

[0059] When more than two outer ringless cylindrical roller bearing structures 100 are arranged side by side along the axial direction A, a pattern in which two first retaining frames 31 located below the bearing pitch circle and two second retaining frames 32 located above the bearing pitch circle are arranged alternately can be formed in the axial direction A, wherein the two first retaining frames 31 are adjacent and the two second retaining frames 32 are also adjacent, or a pattern in which one first retaining frame 31 located below the bearing pitch circle and one second retaining frame 32 located above the bearing pitch circle are arranged alternately can be formed.

[0060] It is understood that in this disclosure, "plurality" refers to two or more than two, and other quantifiers are similar. "And / or" describes the association relationship of related objects, indicating that three relationships may exist. For example, A and / or B can mean: A exists alone, A and B exist at the same time, and B exists alone. The character " / " generally indicates that the related objects before and after are in an "or" relationship. The singular forms "a", "the" and "the" are also intended to include the plural forms, unless the context clearly indicates otherwise.

[0061] It will be further understood that the terms "first," "second," and the like are used to describe various structures, but these structures should not be limited to these terms. These terms are merely used to distinguish structures of the same type from one another and do not indicate a particular order or degree of importance. In fact, the expressions "first," "second," and the like are fully interchangeable. For example, a first structure could also be referred to as a second structure, and similarly, a second structure could also be referred to as a first structure without departing from the scope of this disclosure.

[0062] It can be further understood that the terms "center", "longitudinal", "lateral", "front", "back", "up", "down", "left", "right", "vertical", "horizontal", "top", "bottom", "inside", "outside", etc., indicating the orientation or position relationship, are based on the orientation or position relationship shown in the accompanying drawings, and are only for the convenience of describing this embodiment and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, be constructed and operate in a specific orientation.

[0063] Those skilled in the art will readily appreciate other embodiments of the present disclosure after considering the specification and practicing the invention disclosed herein. This application is intended to cover any variations, uses, or adaptations of the present disclosure that follow the general principles of the present disclosure and include common knowledge or customary techniques in the art not disclosed herein. The description and examples are to be considered merely as exemplary, and the true scope and spirit of the present disclosure are indicated by the following claims.

[0064] It should be understood that the present disclosure is not limited to the exact structures described above and shown in the drawings, and that various modifications and changes may be made without departing from the scope thereof. The scope of the present disclosure is limited only by the scope of the appended claims.

Claims

1. A cylindrical roller bearing structure (100) without an outer ring for a wind power gearbox, characterized in that: include: An inner ring (10), wherein the outer circumference of the inner ring (10) is provided with a first row of raceways (12) and a second row of raceways (13); A first rolling body (21) and a second rolling body (22) are respectively located in the first row of raceways (12) and the second row of raceways (13); and The first retaining frame (31) and the second retaining frame (32) are used to circumferentially separate the first rolling element (21) of the first row of raceways (12) and the second rolling element (22) of the second row of raceways (13), respectively. The outer diameter of the first retaining frame (31) is smaller than the diameter of the circle on which the center of the first rolling body (21) is located, the inner diameter of the second retaining frame (32) is larger than the diameter of the circle on which the center of the second rolling body (22) is located, and the first retaining frame (31) and the second retaining frame (32) partially overlap in the axial direction A.

2. The outer ringless cylindrical roller bearing structure (100) for a wind power gearbox according to claim 1, characterized in that: The diameter (Dw1) of the first rolling element (21) is equal to the diameter (Dw2) of the second rolling element (22); and The axial length (Lw1) of the first rolling element (21) and the axial length (Lw2) of the second rolling element (22) are equal to or different from each other.

3. The outer ringless cylindrical roller bearing structure (100) for a wind power gearbox according to claim 1, characterized in that: The outer circumference of the inner ring (10) further comprises an intermediate rib (11), wherein the intermediate rib (11) protrudes from the outer circumference of the inner ring (10) in the radial direction (R), and the first row of raceways (12) and the second row of raceways (13) share the intermediate rib (11). The intermediate rib (11) overlaps with the first retaining frame (31) and the second retaining frame (32) in the axial direction (A), and the axial width (BS1) of the intermediate rib (11) satisfies: BS1≥X1+μ or BS1≥X2+μ, X1 and X2 are respectively the widths of the first retaining frame (31) and the second retaining frame (32). The axial overlapping length of the holder (31) and the second holder (32) with the intermediate rib (11), μ is the axial movement amount of the first holder (31) / the second holder (32).

4. The outer ringless cylindrical roller bearing structure (100) for a wind power gearbox according to claim 3, characterized in that: The middle rib (11) and the inner ring (10) are integrally formed.

5. The outer ringless cylindrical roller bearing structure (100) for a wind power gearbox according to claim 2, characterized in that: The first retaining frame (31) and the second retaining frame (32) are spaced apart in the radial direction (R), and the spacing distance e satisfies: 0≤e≤0.1Dw1 or 0≤e≤0.1Dw2, where Dw1 and Dw2 are the diameters of the first rolling element (21) and the second rolling element (22), respectively.

6. The outer ringless cylindrical roller bearing structure (100) for a wind power gearbox according to claim 4, characterized in that: The thickness (S1) of the first retaining frame (31) is equal to the thickness (S2) of the second retaining frame (32).

7. The outer ringless cylindrical roller bearing structure (100) for a wind power gearbox according to claim 1, characterized in that: The outer ringless cylindrical roller bearing structure 100 further includes: A fixed rib (14), the fixed rib (14) being located at one axial end of the inner ring (10), forming a first row of raceways (12) with the intermediate rib (11), and being used for abutting against the first rolling element (21); A movable retaining ring (40) is located at the other axial end of the inner ring (10), forms a second row of raceways (13) with the middle retaining edge (11), and is used to abut against the second rolling element (22).

8. The outer ringless cylindrical roller bearing structure (100) for a wind power gearbox according to claim 7, characterized in that: The fixed rib (14) and the inner ring (10) are integrally formed; and The movable retaining ring (40) is detachably connected to the inner ring (10) by means of interference fit, clamping ring connection or fasteners.

9. The outer ringless cylindrical roller bearing structure (100) for a wind power gearbox according to claim 1, characterized in that: When the two cylindrical roller bearing structures (100) without outer rings are arranged side by side along the axial direction (A), The two first rolling elements (21) of the two outer ringless cylindrical roller bearing structures (100) are adjacent to each other, or the two second rolling elements (22) of the two outer ringless cylindrical roller bearing structures (100) are adjacent to each other.

10. The outer ringless cylindrical roller bearing structure (100) for a wind power gearbox according to claim 1, characterized in that: The second retaining frame (32) is guided by the second rolling element (22); or The second cage (32) is guided by the outer ring.

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