Double-row cylindrical roller bearing, gear box and fan

Abstract

The utility model relates to the technical field of gear boxes, in particular to a double-row cylindrical roller bearing, a gear box and a fan. The two double-row cylindrical roller bearings are symmetrically arranged on a pin shaft of a planet carrier in the gearbox, and the planet wheel can be rotationally installed on the pin shaft through the two double-row cylindrical roller bearings. The double-row cylindrical roller bearing comprises a bearing inner ring, a bearing outer ring, a retainer, a first row of rollers and a second row of rollers, the first row of rollers and the second row of rollers are asymmetrically arranged on the retainer, the first row of rollers are close to the outer side of the planet wheel, and the second row of rollers are close to the inner side of the planet wheel; the axial length of the first row of rollers is greater than that of the second row of rollers; the modification amount of the rolling surfaces, close to the outer side of the planet wheel, of the first-row rollers is larger than that of the rolling surfaces, close to the inner side of the planet wheel, of the first-row rollers, and the shapes of the second-row rollers are symmetrically arranged. The gearbox and the fan comprise the double-row cylindrical roller bearing, so that the stress borne by the rollers is uniformly distributed, and the failure risk of the rollers is reduced.

Description

Technical Field

[0001] The utility model relates to the technical field of gear boxes, in particular to a double-row cylindrical roller bearing, a gear box and a fan. Background Art

[0002] With the continuous development of the wind power industry, the power of wind turbines has continued to increase, and gearboxes are one of the essential components in wind turbines (hereinafter referred to as wind turbines). Double-row cylindrical roller bearings are a common bearing used in wind power gearboxes. They are used in planetary stages and arranged on the pins of the planetary carrier to achieve normal transmission of the planetary gears. When the speed is low and the load is heavy, two sets of double-row cylindrical roller bearings are required to carry the load together, and four-row rollers are used to support the planetary gears. To ensure interchangeability, the size of the four-row rollers and the modification amount of the rolling surface are the same.

[0003] The existing wind turbine gearbox has a large system deformation during the torque transmission process. The system deformation will cause the gear meshing to have an offset load. Under the offset load condition, the roller stress near the outer side of the planetary gear is greater, which makes the roller near the outer side of the planetary gear more likely to fail. Even when the planetary gear is evenly stressed, the stress concentration at both ends of the planetary gear axis is more obvious, resulting in the stress of the roller near the outer side of the planetary gear being significantly higher than the stress of the roller near the inner side of the planetary gear, further accelerating the failure risk of the roller near the outer side of the planetary gear. Utility Model Content

[0004] The utility model aims to provide a double-row cylindrical roller bearing, a gear box and a fan, so that the stress on the rollers in the double-row cylindrical roller bearing is evenly distributed, thereby reducing the risk of roller failure.

[0005] To achieve this purpose, the technical solution adopted by the utility model is:

[0006] Double-row cylindrical roller bearings, two of which are symmetrically arranged on the pins of the planetary carrier in the gearbox, and the planetary gear can be rotatably mounted on the pins through the two double-row cylindrical roller bearings;

[0007] The double-row cylindrical roller bearing includes a bearing inner ring, a bearing outer ring, a retaining frame, a first row of rollers and a second row of rollers. The first row of rollers and the second row of rollers are asymmetrically arranged on the retaining frame. The first row of rollers is close to the outer side of the planetary gear, and the second row of rollers is close to the inner side of the planetary gear. The axial length of the first row of rollers is greater than the axial length of the second row of rollers. The shaping amount of the rolling surface of the first row of rollers close to the outer side of the planetary gear is greater than the shaping amount of the rolling surface of the first row of rollers close to the inner side of the planetary gear, and the outer shapes of the second row of rollers are symmetrically arranged.

[0008] As a preferred solution, the axial length of the first row of rollers is L1, the axial length of the second row of rollers is L2, and 1<L1 / L2≤1.2.

[0009] As a preferred solution, the modification amount y1 of the rolling surface of the first row of rollers is:

[0010]

[0011] Among them, b1 is the effective length of the first row of rollers, B0 is the adjustable coefficient, b1>B0>b1 / 2, x / b1∈[-0.5,0.5], k1 and k2 are coefficients for controlling the amount of shaping, k1<0, k2>0, p1 and p2 are exponential coefficients, p1∈[0,5], p2∈[0,15].

[0012] As a preferred embodiment, a radial plane passing through the center point of the first row of rollers divides the first row of rollers into a first cylindrical segment and a second cylindrical segment. Within the effective length of the first row of rollers, the shaping amount of the rolling surface of the first cylindrical segment gradually decreases along the direction from the outer side of the planetary gear toward the inner side of the planetary gear, and the shaping amount of the rolling surface of the second cylindrical segment gradually decreases along the direction from the outer side of the planetary gear toward the inner side of the planetary gear and then gradually increases.

[0013] As a preferred solution, the modification amount y1 of the rolling surface of the first row of rollers is ≤100 μm.

[0014] As a preferred solution, the modification amount y2 of the rolling surface of the second row of rollers is:

[0015]

[0016] Among them, b2 is the effective length of the second row of rollers, B0 is the adjustable coefficient, b2>B0>b2 / 2, x / b2∈[-0.5,0.5], k2 is the coefficient for controlling the amount of shaping, k2>0, p1 and p2 are exponential coefficients, p1∈[0,5], p2∈[0,15].

[0017] As a preferred solution, both ends of the first row of rollers in the axial direction and both ends of the second row of rollers in the axial direction are chamfered.

[0018] As a preferred solution, one axial end of the first row of rollers close to the outer side of the planetary gear has a chamfered right angle structure, and one axial end of the first row of rollers close to the inner side of the planetary gear has a chamfered corner structure.

[0019] As a preferred solution, both axial ends of the second row of rollers have rounded corners.

[0020] The gearbox comprises a planet carrier, planetary wheels and at least two of the above-mentioned double-row cylindrical roller bearings.

[0021] A wind turbine comprises a generator, a wind turbine body and the above-mentioned gear box, wherein the generator is transmission-connected to the wind turbine body through the gear box.

[0022] The beneficial effects of the utility model are:

[0023] The double-row cylindrical roller bearing proposed by the utility model has a first row of rollers and a second row of rollers asymmetrically arranged on the retaining frame. The axial length of the first row of rollers close to the outer side of the planetary gear is greater than the axial length of the second row of rollers close to the inner side of the planetary gear, so as to improve the load-bearing capacity of the first row of rollers and avoid stress concentration. At the same time, the shape of the first row of rollers is asymmetrically arranged, and the shaping amount of the rolling surface of the first row of rollers close to the outer side of the planetary gear is greater than the shaping amount of the rolling surface of the first row of rollers close to the inner side of the planetary gear, which effectively reduces the maximum stress of the first row of rollers, so that the stress of the first row of rollers and the second row of rollers is evenly distributed, reducing the failure risk of the two rows of rollers.

[0024] The gearbox proposed in the utility model includes the above-mentioned double-row cylindrical roller bearing, so that the stress on the first row of rollers and the second row of rollers of the double-row cylindrical roller bearing is evenly distributed, reducing the failure risk of the two rows of rollers and increasing the life of the gearbox.

[0025] The fan provided by the utility model includes the above-mentioned gear box, so that the stress on the first row of rollers and the second row of rollers of the double-row cylindrical roller bearing is evenly distributed, thereby reducing the failure risk of the two rows of rollers and increasing the service life of the fan. BRIEF DESCRIPTION OF THE DRAWINGS

[0026] Figure 1 It is a schematic diagram of the partial structure inside the gear box provided by the embodiment of the utility model;

[0027] Figure 2 It is a schematic diagram of the modification of the first row of rollers and the second row of rollers provided in an embodiment of the utility model;

[0028] Figure 3 It is a cross-sectional view of a double-row cylindrical roller bearing provided in an embodiment of the utility model.

[0029] The names and numbers of the components in the figure are as follows:

[0030] 1. Planet carrier; 2. Planet gear; 3. Double-row cylindrical roller bearing; 31. Bearing inner ring; 33. Cage; 34. First row of rollers; 35. Second row of rollers; 4. Pin. DETAILED DESCRIPTION

[0031] In order to make the technical problems solved by the present invention, the technical solutions adopted and the technical effects achieved clearer, the technical solutions of the present invention are further described below in conjunction with the accompanying drawings and through specific implementation methods. It is understood that the specific embodiments described herein are only used to explain the present invention, rather than to limit the present invention. It should also be noted that, for the convenience of description, only the parts related to the present invention are shown in the accompanying drawings, rather than all of them.

[0032] In the description of the present invention, unless otherwise clearly specified and limited, the terms "connected", "connected", and "fixed" should be understood in a broad sense, for example, it can be a fixed connection, a detachable connection, or an integral connection; it can be a mechanical connection or an electrical connection; it can be a direct connection or an indirect connection through an intermediate medium, it can be the internal connection of two elements or the interaction relationship between two elements. For ordinary technicians in this field, the specific meanings of the above terms in the present invention can be understood according to specific circumstances.

[0033] In the present utility model, unless otherwise clearly specified and limited, a first feature being "above" or "below" a second feature may include that the first and second features are in direct contact, or may include that the first and second features are not in direct contact but are in contact through another feature between them. Moreover, a first feature being "above", "above" and "above" a second feature includes that the first feature is directly above and obliquely above the second feature, or simply indicates that the first feature is higher in level than the second feature. A first feature being "below", "below" and "below" a second feature includes that the first feature is directly below and obliquely below the second feature, or simply indicates that the first feature is lower in level than the second feature.

[0034] In the description of this embodiment, the terms "upper", "lower", "right", "left" and other directions or positional relationships are based on the directions or positional relationships shown in the drawings, and are only for the convenience of description and simplified operation, rather than indicating or implying that the device or element referred to must have a specific direction, be constructed and operated in a specific direction, and therefore cannot be understood as a limitation of the present invention. In addition, the terms "first" and "second" are only used to distinguish in the description and have no special meaning.

[0035] The technical solution of the utility model is further explained below with reference to the accompanying drawings and through specific implementation methods.

[0036] This embodiment proposes a gearbox for use in a wind turbine, but is not limited thereto. The gearbox may also be used in other devices or systems requiring transmission, which is not specifically limited herein.

[0037] like Figure 1As shown, the gearbox includes a planet carrier 1 and a planet wheel 2, and the planet wheel 2 is rotatably mounted on a pin shaft 4 of the planet carrier 1 through a bearing. In order to improve the bearing capacity of the bearing, two bearings need to be symmetrically arranged on the pin shaft 4.

[0038] Existing bearings are generally symmetrical double-row cylindrical roller bearings, that is, the size of the four-row rollers and the modification amount of the rolling surface are the same to ensure interchangeability. The gearbox has a large system deformation during the torque transmission process. The system deformation will cause the gear meshing to have an unbalanced load. Under the unbalanced load condition, the stress of the rollers close to the outside of the planetary gear 2 will be greater, causing the rollers close to the outside of the planetary gear 2 to fail more easily. Even when the planetary gear 2 is evenly stressed, the stress concentration at the two axial ends of the planetary gear 2 is more obvious, causing the stress of the rollers close to the outside of the planetary gear 2 to be significantly higher than the stress of the rollers close to the inside of the planetary gear 2, further accelerating the failure risk of the rollers close to the outside of the planetary gear 2.

[0039] To solve the above problems, Figure 1 and Figure 2 As shown, this embodiment also proposes a double-row cylindrical roller bearing 3, two double-row cylindrical roller bearings 3 are symmetrically arranged on the pin 4 of the planetary carrier 1 in the gearbox, and the planetary gear 2 can be rotatably mounted on the pin 4 through the two double-row cylindrical roller bearings 3. The double-row cylindrical roller bearing 3 includes a bearing inner ring 31, a retainer 33, a first row of rollers 34 and a second row of rollers 35. The first row of rollers 34 and the second row of rollers 35 are asymmetrically arranged on the retainer 33, the first row of rollers 34 are close to the outside of the planetary gear 2, and the second row of rollers 35 are close to the inside of the planetary gear 2. The axial length of the first row of rollers 34 is greater than the axial length of the second row of rollers 35. The modification amount of the rolling surface of the first row of rollers 34 close to the outside of the planetary gear 2 is greater than the modification amount of the rolling surface of the first row of rollers 34 close to the inside of the planetary gear 2, and the outer shape of the second row of rollers 35 is symmetrically arranged. The first row of rollers 34 and the second row of rollers 35 are asymmetrically arranged on the retainer 33. The axial length of the first row of rollers 34 near the outside of the planetary gear 2 is greater than the axial length of the second row of rollers 35 near the inside of the planetary gear 2, so as to improve the load-bearing capacity of the first row of rollers 34 and avoid stress concentration. At the same time, the shape of the first row of rollers 34 is set asymmetrically, and the modification amount of the rolling surface of the first row of rollers 34 near the outside of the planetary gear 2 is greater than the modification amount of the rolling surface of the first row of rollers 34 near the inside of the planetary gear 2, which effectively reduces the maximum stress of the first row of rollers 34, so that the stress of the first row of rollers 34 and the second row of rollers 35 is evenly distributed, reducing the failure risk of the two rows of rollers.

[0040] It should be noted that the axial length of the first row of rollers 34 is L1, and the axial length of the second row of rollers 35 is L2, 1<L1 / L2≤1.2. In this embodiment, the axial length of the first row of rollers 34 is about 1.2 times the axial length of the second row of rollers 35, so that the first row of rollers 34 and the second row of rollers 35 have appropriate axial lengths to make the stress distribution of the two rows of rollers more uniform. When L1 / L2>1.2, the axial length of the second row of rollers 35 is too small, resulting in too small load-bearing capacity of the second row of rollers 35, and stress concentration is prone to occur.

[0041] In this embodiment, the first row of rollers 34 and the second row of rollers 35 have the same diameter and different axial lengths, and the first row of rollers 34 and the second row of rollers 35 adopt different shaping methods. Specifically, the shaping of the first row of rollers 34 is asymmetric, and a logarithmic shaping method and a linear shaping method are used to make the shape of the first row of rollers 34 asymmetric. The shaping of the second row of rollers 35 is symmetric, and a logarithmic shaping method is used to make the shape of the second row of rollers 35 symmetrical.

[0042] Specifically, Figure 2 As shown, the modification amount y1 of the rolling surface of the first row of rollers 34 is:

[0043]

[0044] Wherein, b1 is the effective length of the first row of rollers 34, B0 is an adjustable coefficient, b1>B0>b1 / 2, x / b1∈[-0.5,0.5], k1 and k2 are coefficients for controlling the amount of modification, k1<0, k2>0, p1 and p2 are exponential coefficients, p1∈[0,5], p2∈[0,15]. By adjusting the values ​​of B0, k1, k2, p1 and p2, the first row of rollers 34 with different amounts of modification are obtained, and then the stress distribution of the first row of rollers 34 is truly simulated by simulation analysis software to obtain the optimal amount of modification. The above simulation optimization processes are all conventional processing methods in this field and will not be described in detail here. The above-mentioned method of optimizing the amount of modification can effectively reduce the maximum stress of the first row of rollers 34, so that the stress distribution of the first row of rollers 34 is more uniform.

[0045] like Figure 2 As shown in the figure, the center of the first row of rollers 34 is taken as the coordinate origin 0, and the solid line in the figure represents the modified amount of the first row of rollers 34 after optimization. Specifically, the radial plane passing through the center point of the first row of rollers 34 divides the first row of rollers 34 into a first cylindrical section and a second cylindrical section. Within the effective length of the first row of rollers 34, the modified amount of the rolling surface of the first cylindrical section gradually decreases from the outer side of the planetary gear 2 to the inner side of the planetary gear 2, and the modified amount of the rolling surface of the second cylindrical section gradually decreases from the outer side of the planetary gear 2 to the inner side of the planetary gear 2 and then gradually increases. According to Figure 2 The solid lines in the figure are used to modify the first row of rollers 34 so that the first row of rollers 34 can adjust their outer contours according to the stress they are subjected to, thereby effectively reducing the maximum stress of the first row of rollers 34 and improving the uniformity of stress distribution on the first row of rollers 34.

[0046] In this embodiment, the rolling surface modification amount y1 of the first row of rollers 34 is ≤100μm, so as to avoid excessive modification of the rolling surface of the first row of rollers 34, thereby avoiding excessive asymmetry of the shape of the first row of rollers 34, so as to ensure the stability of the first row of rollers 34 when rolling on the inner ring 31 of the bearing.

[0047] like Figure 2 As shown, the modification amount y2 of the rolling surface of the second row of rollers 35 is:

[0048]

[0049] Wherein, b2 is the effective length of the second row of rollers 35, B0 is an adjustable coefficient, b2>B0>b2 / 2, x / b2∈[-0.5,0.5], k2 is the coefficient for controlling the amount of modification, k2>0, p1 and p2 are exponential coefficients, p1∈[0,5], p2∈[0,15]. By adjusting the values ​​of B0, k1, k2, p1 and p2, the second row of rollers 35 with different amounts of modification are obtained, and the stress distribution of the second row of rollers 35 is truly simulated by simulation analysis software to obtain the optimal amount of modification. The above simulation optimization process is a conventional processing method in this field and will not be described in detail here.

[0050] like Figure 2 As shown in FIG. 1 , the center of the second row of rollers 35 is taken as the coordinate origin 0, and the dotted line in the figure represents the modified amount of the second row of rollers 35 after optimization. Figure 2 The dotted lines in the figure are used to modify the second row of rollers 35 so that the second row of rollers 35 can adjust their outer contours according to the stress they are subjected to, thereby effectively reducing the maximum stress of the second row of rollers 35 and improving the uniformity of stress distribution on the second row of rollers 35.

[0051] like Figure 3 As shown, the double-row cylindrical roller bearing 3 has no bearing outer ring, and the inner ring of the planetary gear 2 forms a raceway for two rows of rollers with the bearing inner ring 31. Of course, in other embodiments, the double-row cylindrical roller bearing 3 may also have a bearing outer ring, in which case the bearing outer ring forms a raceway for two rows of rollers with the bearing inner ring 31. The inner ring of the planetary gear 2 is sleeved on the bearing outer ring.

[0052] Furthermore, both axial ends of the first row of rollers 34 and both axial ends of the second row of rollers 35 are chamfered to avoid stress concentration at both axial ends of the two rows of rollers, and at the same time, burrs at both axial ends of the two rows of rollers can be removed to avoid scratching the surface of the bearing inner ring 31 and the inner ring surface of the planetary gear 2.

[0053] Specifically, Figure 3 As shown, the axial end of the first row of rollers 34 close to the outer side of the planetary gear 2 has a chamfered right angle structure, and the axial end of the first row of rollers 34 close to the inner side of the planetary gear 2 has a chamfered corner structure. Both ends of the axial direction of the second row of rollers 35 have a chamfered corner structure. Since the axial lengths of the first row of rollers 34 and the second row of rollers 35 are different, the two rollers can be intuitively and quickly distinguished, avoiding the misalignment of the installation of the first row of rollers 34 and the second row of rollers 35. At the same time, since the chamfered structures at both ends of the axial direction of the first row of rollers 34 are different (one is a chamfered right angle structure and the other is a chamfered corner structure), the position and direction of the two rows of rollers can be effectively distinguished, so as to provide precise guidance for the installation of the double row cylindrical roller bearing 3 on the pin 4, avoid installation errors, improve the installation efficiency of the double row cylindrical roller bearing 3, and realize the accurate installation of the double row cylindrical roller bearing 3.

[0054] This embodiment also provides a wind turbine, which includes a generator, a wind turbine body and the above-mentioned gearbox, wherein the generator is connected to the wind turbine body through the gearbox to realize the wind power generation process. By using a gearbox with a double-row cylindrical roller bearing 3, the stress on the first row of rollers 34 and the second row of rollers 35 of the double-row cylindrical roller bearing 3 is evenly distributed, thereby reducing the failure risk of the two rows of rollers and increasing the life of the wind turbine.

[0055] The above embodiments are only to illustrate the basic principles and characteristics of the present invention. The present invention is not limited by the above embodiments. Without departing from the spirit and scope of the present invention, the present invention may be subject to various changes and modifications, which are within the scope of the present invention. The scope of protection of the present invention is defined by the attached claims and their equivalents.

Claims

1. Double row cylindrical roller bearing, characterized in that: The two double-row cylindrical roller bearings are symmetrically arranged on the pin shaft (4) of the planetary carrier (1) in the gear box, and the planetary gear (2) can be rotatably mounted on the pin shaft (4) through the two double-row cylindrical roller bearings; The double-row cylindrical roller bearing comprises a bearing inner ring (31), a cage (33), a first row of rollers (34) and a second row of rollers (35); the first row of rollers (34) and the second row of rollers (35) are asymmetrically arranged on the cage (33); the first row of rollers (34) are close to the outer side of the planetary gear (2); the second row of rollers (35) are close to the inner side of the planetary gear (2); the axial length of the first row of rollers (34) is greater than the axial length of the second row of rollers (35); the modification amount of the rolling surface of the first row of rollers (34) close to the outer side of the planetary gear (2) is greater than the modification amount of the rolling surface of the first row of rollers (34) close to the inner side of the planetary gear (2); and the outer shapes of the second row of rollers (35) are symmetrically arranged.

2. The double row cylindrical roller bearing according to claim 1, characterized in that: The axial length of the first row of rollers (34) is L1, and the axial length of the second row of rollers (35) is L2, 1<L1 / L2≤1.

2.

3. The double row cylindrical roller bearing according to claim 1, characterized in that: The modification amount y1 of the rolling surface of the first row of rollers (34) is: Wherein, b1 is the effective length of the first row of rollers (34), B0 is an adjustable coefficient, b1>B0>b1 / 2, x / b1∈[-0.5,0.5], k1 and k2 are coefficients for controlling the amount of shaping, k1<0, k2>0, p1 and p2 are exponential coefficients, p1∈[0,5], p2∈[0,15].

4. The double row cylindrical roller bearing according to claim 3, characterized in that: A radial plane passing through the center point of the first row of rollers (34) divides the first row of rollers (34) into a first cylindrical section and a second cylindrical section. Within the effective length of the first row of rollers (34), the modification amount of the rolling surface of the first cylindrical section gradually decreases in a direction from the outer side of the planetary wheel (2) toward the inner side of the planetary wheel (2), and the modification amount of the rolling surface of the second cylindrical section gradually decreases in a direction from the outer side of the planetary wheel (2) toward the inner side of the planetary wheel (2) and then gradually increases.

5. The double row cylindrical roller bearing according to claim 3, characterized in that: The modification amount y1 of the rolling surface of the first row of rollers (34) is ≤100 μm.

6. The double row cylindrical roller bearing according to claim 1, characterized in that: The modification amount y2 of the rolling surface of the second row of rollers (35) is: Wherein, b2 is the effective length of the second row of rollers (35), B0 is an adjustable coefficient, b2>B0>b2 / 2, x / b2∈[-0.5,0.5], k2 is a coefficient for controlling the amount of shaping, k2>0, p1 and p2 are exponential coefficients, p1∈[0,5], p2∈[0,15].

7. The double row cylindrical roller bearing according to claim 1, characterized in that: Both axial ends of the first row of rollers (34) and both axial ends of the second row of rollers (35) are chamfered.

8. The double row cylindrical roller bearing according to claim 7, characterized in that: The axial end of the first row of rollers (34) close to the outer side of the planetary gear (2) has a chamfered right angle structure, and the axial end of the first row of rollers (34) close to the inner side of the planetary gear (2) has a chamfered corner structure; both axial ends of the second row of rollers (35) have a chamfered corner structure.

9. Gear box, characterized in that, The invention comprises a planet carrier (1), a planet wheel (2) and at least two double-row cylindrical roller bearings according to any one of claims 1 to 8.

10. A fan, characterized in that: It comprises a generator, a wind turbine body and the gear box as claimed in claim 9, wherein the generator is drivingly connected to the wind turbine body through the gear box.

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