A full complement cylindrical roller bearing with a special end face

Abstract

The utility model relates to a kind of special-shaped end face full-size cylindrical roller bearing, comprising: inner ring, two rows of cylindrical roller outer diameter rolling contact in the raceway of inner ring;Planetary gear with wind power driver is located in the outer direction of inner ring and is matched with cylindrical roller outer diameter;Two rows of cylindrical roller inner end face between and close to the inner diameter surface of planetary gear are respectively provided with flat baffle, two flat baffle are connected with the inner diameter of planetary gear by lock ring;The inner diameter of the inner ring is matched with the center shaft of wind power driver, the bearing is designed as special-shaped end face design mode, i. e. one end face uses big fillet transition, the other end is plane end face design;And the end face position of the big fillet transition of the bearing is also designed as the big fillet transition matched with the end face of the big fillet transition of the bearing, to reduce the contact stress of planetary gear shoulder, avoid the risk that stress concentration is too large and leads to the fracture of shoulder, to improve the use performance and demand of fan yaw and variable pitch driver.

Description

Technical Field

[0001] This utility model relates to a full complement cylindrical roller bearing with irregular end face, which is used in wind turbine drives and belongs to the field of bearing technology. Background Technology

[0002] As the driving device for adjusting the windward angle of the wind turbine blades, wind turbine yaw and pitch drives are gradually developing towards higher torque and more compact structures with the upgrading to megawatt-level specifications, which also places increasingly higher demands on the performance of the bearings within them. Yaw and pitch drives typically incorporate one to four-stage planetary reduction systems. Due to the advantages of full complement cylindrical bearings—small size, lightweight, and high load-bearing capacity—they have been widely used in these fields in recent years. For example... Figure 6 The diagram shown is a schematic of a wind turbine drive. Positions 2, 3, 4, and 5 represent the first, second, third, and fourth stage planetary gears, respectively, and the bearings in the planetary gears are full complement cylindrical roller bearings.

[0003] In existing structures, the inner ring end face design of conventional cylindrical bearings is usually symmetrical, which facilitates machining and installation. Wind turbine actuators with large-stage planetary gear systems near the output end typically operate under harsh conditions, with high loads and large overturning moments. During simulation calculations, stress concentration at the planetary gear shoulders is particularly high, even posing a risk of breakage. Utility Model Content

[0004] In view of the problem of excessive stress at the planetary gear shoulder in the yaw and pitch drive of the wind turbine mentioned above, the purpose of this utility model is to provide a full complement cylindrical roller bearing with an irregular end face. By designing the bearing structure, the bearing end face is designed with a large arc transition form. The large arc of the bearing end face matches the planetary gear shoulder, thereby reducing the contact stress at the planetary gear shoulder, preventing the risk of breakage, and meeting the usage requirements of the yaw and pitch drive of the wind turbine.

[0005] To achieve the above objectives, the technical solution adopted by this utility model is as follows: a full complement cylindrical roller bearing with irregular end faces, comprising: an inner ring, wherein two raceways are formed on the outer diameter of the inner ring to mate with two rows of cylindrical rollers, and a retaining edge is formed between the two raceways; the outer diameters of the two rows of cylindrical rollers roll in contact with the raceways of the inner ring; a planetary gear of a wind turbine actuator is located outside the inner ring and mates with the outer diameter of the cylindrical rollers, the inner diameter of the planetary gear is a straight plane and directly contacts the outer diameter of the two rows of cylindrical rollers; flat retaining rings are respectively provided between the inner end faces of the two rows of cylindrical rollers and near the inner diameter of the planetary gear, and the two flat retaining rings are connected to the inner diameter of the planetary gear by a locking ring; a central shaft of the wind turbine actuator is fitted on the inner diameter of the inner ring, and one end face of the inner ring and one end shoulder of the central shaft form an arc-shaped fillet transition fit; Furthermore, the two end faces of the inner ring are asymmetrically designed, that is, one end face is an irregularly shaped end face with rounded corners, and the other end face is a planar design. Furthermore, the inner ring's end face (arc-shaped rounded corner) and the central shaft shoulder's rounded corner transition fit adopt a large rounded corner transition fit, and the inner ring's end face's flat design fits the central shaft with a retaining ring structure.

[0006] Furthermore, at the shoulder of the central axis, which is in the same direction as the inner ring's rounded corner irregular end face, a smooth rounded arc is formed, and the curvature of this rounded arc is greater than that of the inner ring's rounded corner irregular end face.

[0007] Furthermore, the structure of the inner ring's arc-shaped rounded corner irregular end face is a design form of slope-corner-slope-reverse arc; Furthermore, the sequence of slope-angle-slope-reverse arc is the extension sequence from the inner diameter surface of the inner ring to the end face surface. Furthermore, the slope-angle-slope-reverse arc refers to the first slope, the large rounded corner, the second slope, and the reverse arc, respectively, and they transition smoothly to each other; the reverse arc is an inwardly concave arc opposite to the direction of the large rounded corner, and the area between the outer end point of the reverse arc and the outer diameter of the inner circle is a flat end face; the horizontal distance between the inner end point and the outer end point of the reverse arc is the depth of the reverse arc. Furthermore, the extension line of the first slope forms a 15° angle with the inner diameter of the inner ring, a 15° slope design; Furthermore, a 15° angle is formed between the extension of the inner end point of the second slope and the reverse circular arc. Furthermore, the large fillet radius R is 5.5mm.

[0008] Furthermore, the angle between the outer endpoint of the reverse circular arc and the extension line of the flat end face is set to 60°. Furthermore, the specific method of connecting the two flat retaining rings to the inner diameter of the planetary gear via the locking ring is as follows: the inner diameter of the planetary gear is provided with a groove that matches the width of the locking ring. During assembly, the locking ring is fitted in the groove and both ends of the locking ring are fitted with the inner end faces of the two flat retaining rings. Furthermore, a mounting groove for inserting a retaining ring is provided on the outer diameter of the central shaft corresponding to the position of the inner ring plane end face. The retaining ring is inserted into the mounting groove so that the inner end face of the retaining ring abuts against the inner ring plane end face, thereby limiting the inner ring. Furthermore, the inner ring plane end face and the inner diameter surface form a rounded chamfer design, and the size of the rounded chamfer is much smaller than the radius of the large rounded corner of the inner ring's arc-shaped irregular end face.

[0009] The beneficial effects of this utility model are: The bearing is designed with an irregular end face design, that is, one end face has a large rounded corner transition and the other end face is a flat end face design; and the planetary gear shaft shoulder corresponding to the end face position of the large rounded corner transition of the bearing is also designed with a large rounded corner transition to match the end face of the bearing, thereby reducing the contact stress at the planetary gear shaft shoulder, avoiding the risk of breakage at the shaft shoulder due to excessive stress concentration, and thus improving the performance and requirements of the wind turbine yaw and pitch drive. Attached Figure Description

[0010] Figure 1 This is a structural diagram of the bearing of this utility model.

[0011] Figure 2 This is a schematic diagram showing the fit between the bearing of this utility model and the central shaft of the wind turbine drive.

[0012] Figure 3 This is a detailed view of the large fillet position of the bearing of this utility model.

[0013] Figure 4 for Figure 3 A magnified view of a portion of the image.

[0014] Figure 5 This is a structural diagram of the bearing of this utility model, where the inner ring is designed with a flat end face.

[0015] Figure 6 This is a schematic diagram of a certain type of fan drive.

[0016] In the diagram, 1. Inner ring, 2. Cylindrical roller, 3. Planetary gear, 4. Flat retaining ring, 5. Locking ring, 6. Central shaft, 7. Retaining ring, 9. Rounded corner arc, 1.1. First ramp, 1.2. Large rounded corner, 1.3. Second ramp, 1.4. Reverse arc, 1.5. Outer end point, 1.6. Flat end face, 1.7. Inner end point, h. Depth of reverse arc, 1.8. Inner ring inner diameter, 1.6.1. Extension line of flat end face, 1.9. Inner ring plane end face, 1.10. Rounded chamfer. Detailed Implementation

[0017] To make the above-mentioned objects, features, and advantages of this utility model more apparent and understandable, the specific embodiments of this utility model will be described in detail below with reference to the accompanying drawings. Many specific details are set forth in the following description to provide a full understanding of this utility model. However, this utility model can be implemented in many other ways different from those described herein, and those skilled in the art can make similar modifications without departing from the spirit of this utility model. Therefore, this utility model is not limited to the specific embodiments disclosed below.

[0018] like Figure 1-5The illustrated non-circular end face full complement cylindrical roller bearing includes: an inner ring 1, on which two raceways are formed on the outer diameter to mate with two rows of cylindrical rollers 2, and a retaining flange is formed between the two raceways. The outer diameters of the two rows of cylindrical rollers 2 roll in contact with the raceways of the inner ring 1; a planetary gear 3 for a wind turbine actuator is located outside the inner ring 1 and mates with the outer diameters of the cylindrical rollers 2, the inner diameter of the planetary gear 3 is a straight plane and directly contacts the outer diameters of the two rows of cylindrical rollers 2; flat retaining rings 4 are respectively provided between the inner end faces of the two rows of cylindrical rollers 2 and near the inner diameter of the planetary gear 3, and the two flat retaining rings 4 are connected to the inner diameter of the planetary gear 3 by locking rings 5; a central shaft 6 for the wind turbine actuator is fitted on the inner diameter of the inner ring 1, and one end face of the inner ring 1 and one end shoulder of the central shaft 6 form an arc-shaped fillet transition fit; Furthermore, the two end faces of the inner ring 1 are asymmetrically designed, that is, one end face is an irregularly shaped end face with rounded corners, and the other end face is a planar design. Furthermore, the bearings in this design feature a full complement double-row cylindrical roller bearing design without an outer ring. Furthermore, the end face of the inner ring 1 (arc-shaped rounded corner) and the shoulder of the central shaft 6 are fitted with a large rounded corner transition fit, and the flat end of the end face of the inner ring 1 is fitted with the central shaft 6 using a retaining ring 7 structure.

[0019] Furthermore, a smooth-transition rounded arc 9 is formed at the shoulder of the central axis 6 in the same direction as the arc-shaped rounded end face of the inner ring 1. The curvature of this rounded arc 9 is greater than that of the arc-shaped rounded end face of the inner ring 1.

[0020] Furthermore, the structure of the arc-shaped rounded corner irregular end face of the inner ring 1 is a design form of slope-corner-slope-reverse arc; Furthermore, the sequence of slope-angle-slope-reverse arc is the extension sequence from the inner diameter surface of the inner ring 1 to the end face surface. Furthermore, the slope-angle-slope-reverse arc refers to the first slope 1.1, the large rounded corner 1.2, the second slope 1.3, and the reverse arc 1.4, which are smoothly transitioned to each other; the reverse arc 1.4 is an inwardly concave arc opposite in direction to the large rounded corner 1.2, and the area between the outer end point 1.5 of the reverse arc 1.4 and the outer diameter of the inner circle 1 is a flat end face 1.6; the horizontal distance between the inner end point 1.7 and the outer end point 1.6 of the reverse arc 1.4 is the depth h of the reverse arc; Furthermore, the extension line of the first ramp 1.1 forms a 15° angle with the inner diameter of the inner ring 1. The 15° ramp design is used for guidance and facilitates bearing installation. Furthermore, a 15° angle is formed between the extension of the inner endpoint 1.7 of the second ramp 1.3 and the reverse circular arc 1.4; Furthermore, the large fillet radius 1.2R is 5.5mm.

[0021] Furthermore, the angle between the outer endpoint 1.5 of the reverse circular arc 1.4 and the extension line 1.6.1 of the flat end face is set to 60°. In the structure described above, the flat end face is 1.6 meters away from H, the reverse arc is 1.4 meters away from r, the depth of the reverse arc is h, and h is 0.3 mm.

[0022] Furthermore, the specific way in which the two flat retaining rings 4 are connected to the inner diameter of the planetary gear 3 via the locking ring 5 is as follows: the inner diameter of the planetary gear 3 is provided with a groove that matches the width of the locking ring 5. During assembly, the locking ring 5 is fitted in the groove and both ends of the locking ring 5 are fitted with the inner end faces of the two flat retaining rings 4. Furthermore, a mounting groove for inserting a retaining ring 7 is provided on the outer diameter of the central shaft 6 corresponding to the position of the inner ring plane end face 1.9. The retaining ring 7 is inserted into the mounting groove so that the inner end face of the retaining ring 7 abuts against the inner ring plane end face 1.9, thereby limiting the inner ring 1. Furthermore, the inner ring plane end face 1.9 forms a rounded chamfer 1.10 with the inner diameter surface. The size of the rounded chamfer 1.10 is much smaller than the radius of the large rounded corner 1.2 of the inner ring 1's arc-shaped irregular end face.

[0023] It should be noted that the tolerance of the large fillet 1.2 (R) of the arc-shaped irregular end face of the inner ring 1 is difficult to control during machining and heat treatment. If R is too large, the distance (H) of the flat end face 1.6 will be too small, resulting in poor contact with the shoulder of the central shaft 6; if R is too large, interference will occur with the shoulder of the central shaft 6. Therefore, the design method is to machine a reverse arc 1.4 (r) at the flat end face 1.6 (H), because the tolerance and heat treatment deformation of the reverse arc 1.4 (r) are small; then machine the large fillet 1.2 (R) to connect and transition with the reverse arc 1.4 (r), ensuring the size of the flat end face 1.6 (H). At the same time, the depth h of the reverse arc can ensure that there is no interference with the shoulder of the central shaft 6 during installation.

[0024] Based on actual installation verification by users, this solution utilizes full complement cylindrical roller bearings with irregular end faces, which can effectively reduce contact stress at the shaft shoulder, and the feedback on the effect is good.

[0025] In the description of this utility model, it should be understood that the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "clockwise", "counterclockwise", "axial", "radial", "circumferential", etc., indicating the orientation or positional relationship are based on the orientation or positional relationship shown in the accompanying drawings, and are only for the convenience of describing this utility model and simplifying the description, and are not intended to indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of this utility model.

[0026] Furthermore, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of indicated technical features. Thus, a feature defined as "first" or "second" may explicitly or implicitly include at least one of that feature. In the description of this utility model, "a plurality of" means at least two, such as two, three, etc., unless otherwise explicitly specified.

[0027] In this utility model, unless otherwise explicitly specified and limited, the terms "installation," "connection," "joining," and "fixing," etc., should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral part; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; they can refer to the internal communication of two components or the interaction between two components, unless otherwise explicitly limited. Those skilled in the art can understand the specific meaning of the above terms in this utility model according to the specific circumstances.

[0028] In this utility model, unless otherwise explicitly specified and limited, "above" or "below" the second feature can mean that the first feature is in direct contact with the second feature, or that the first feature is in indirect contact with the second feature through an intermediate medium. Furthermore, "above," "on top of," and "over" the second feature can mean that the first feature is directly above or diagonally above the second feature, or simply that the first feature is at a higher horizontal level than the second feature. "Below," "below," and "under" the second feature can mean that the first feature is directly below or diagonally below the second feature, or simply that the first feature is at a lower horizontal level than the second feature.

[0029] It should be noted that when an element is referred to as being "fixed to" or "set on" another element, it can be directly on the other element or there may be an intervening element. When an element is considered to be "connected to" another element, it can be directly connected to the other element or there may be an intervening element. The terms "vertical," "horizontal," "upper," "lower," "left," "right," and similar expressions used herein are for illustrative purposes only and do not represent the only possible implementation.

Claims

1. A full complement cylindrical roller bearing with irregular end faces, characterized in that, include: The inner ring has two raceways on its outer diameter that mate with two rows of cylindrical rollers. These raceways form a retaining edge within the inner ring, and the outer diameters of the two rows of cylindrical rollers roll in contact with these raceways. A planetary gear for the wind turbine actuator is located outside the inner ring and mates with the outer diameters of the cylindrical rollers. The inner diameter of the planetary gear is a straight plane and directly contacts the outer diameters of the two rows of cylindrical rollers. Flat retaining rings are provided between the inner end faces of the two rows of cylindrical rollers and near the inner diameter of the planetary gear. These two flat retaining rings are connected to the inner diameter of the planetary gear via locking rings. The inner diameter of the inner ring is fitted with the central shaft of the wind turbine actuator, and one end face of the inner ring forms a rounded transition fit with the shoulder of one end of the central shaft.

2. The irregular end face full complement cylindrical roller bearing according to claim 1, characterized in that: The inner ring has an asymmetrical design at both ends, that is, one end face is an irregularly shaped end face with rounded corners, and the other end face adopts a planar design.

3. A full complement cylindrical roller bearing with irregular end face according to claim 2, characterized in that: The inner ring's end face and the central shaft shoulder have a large rounded corner transition fit, and the inner ring's end face has a retaining ring structure fit with the central shaft.

4. A full complement cylindrical roller bearing with irregular end face according to claim 2, characterized in that: At the shoulder of the central axis, which is in the same direction as the inner ring's rounded corner irregular end face, a smooth rounded arc is formed. The curvature of this rounded arc is greater than that of the inner ring's rounded corner irregular end face.

5. A full complement cylindrical roller bearing with an irregular end face according to claim 4, characterized in that: The inner ring's arc-shaped rounded corner irregular end face has a design form of slope-corner-slope-reverse arc.

6. A full complement cylindrical roller bearing with irregular end face according to claim 5, characterized in that: The slope-angle-slope-reverse arc refers to the first slope, the large rounded corner, the second slope, and the reverse arc, which are smoothly transitioned to each other. The reverse arc is an inwardly concave arc that is opposite to the direction of the large rounded corner. The outer end point of the reverse arc is a flat end face between the outer end point and the outer diameter of the inner circle. The horizontal distance between the inner end point and the outer end point of the reverse arc is the depth of the reverse arc.

7. A full complement cylindrical roller bearing with irregular end face according to claim 6, characterized in that: The extension of the first ramp forms a 15° angle with the inner diameter of the inner circle. The second ramp forms a 15° angle with the extension of the inner end point of the reverse arc.

8. A full complement cylindrical roller bearing with irregular end face according to claim 6, characterized in that: The radius of the large fillet is 5.5mm.

9. A full complement cylindrical roller bearing with irregular end face according to claim 6, characterized in that: The angle between the outer endpoint of the reverse circular arc and the extension line of the flat end face is set to 60°.

10. A full complement cylindrical roller bearing with an irregular end face according to claim 3, characterized in that: A mounting groove for inserting a retaining ring is provided on the outer diameter of the central shaft corresponding to the position of the inner ring plane end face. The retaining ring is inserted into the mounting groove so that the inner end face of the retaining ring abuts against the inner ring plane end face.

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