Main bearing of wind driven generator

Abstract

A main bearing of a wind driven generator comprises a main shaft, a bearing body and a gland, the bearing body and the gland are arranged on the main shaft, the bearing body comprises an outer ring and an inner ring, the main shaft is provided with a containing groove for containing the inner ring, the outer surface of the side, opposite to the main shaft, of the gland is in an arc shape, the outer surface of the other side of the gland is parallel to the adjacent main shaft part, and a gap is reserved between the outer surface of the other side of the gland and the main shaft; an abutting part is arranged at the position, corresponding to the inner ring, of the gland, and the upper edge of the abutting part is flush with the upper edge of the containing groove; fixing holes capable of being spliced are formed in the corresponding positions of the gland and the main shaft, and the gland and the main shaft are fixed by arranging fixing pieces in the fixing holes in a penetrating mode. The utility model has the beneficial effects that the gland with the arc-shaped outer surface on one side opposite to the main shaft can better adapt to the tiny deformation of the bearing seat or the shaft, and more uniform contact pressure is provided. And the stress generated by the arc-shaped gland when the arc-shaped gland is stressed is distributed more uniformly, so that the possibility of stress concentration is reduced, and the axial pre-tightening effect of the bearing is improved.

Description

Technical Field

[0001] The utility model relates to a bearing, in particular to a main bearing of a wind turbine generator. Background Art

[0002] The main bearing of a direct-drive wind turbine generator is a key component in the wind turbine generator, which is responsible for transmitting the mechanical energy generated by the wind turbine to the generator. This kind of bearing usually selects a spherical roller bearing. This kind of bearing is equipped with double-row spherical rollers, the axes of the rollers are inclined to the rotation axis of the bearing, and the outer ring raceway is spherical. Therefore, the rollers can align themselves in the outer ring raceway to compensate for the deflection and concentricity error of the shaft.

[0003] One of the main failure reasons of the main bearing of a direct-drive wind turbine generator is the failure of axial preloading of the bearing. This is because the square gland has insufficient rigidity, resulting in a small pressing force. The square gland has stress concentration due to its right-angle edges, which will cause excessive local pressure during the axial preloading of the bearing, thus affecting the uniform distribution of the preloading force. Summary of the Utility Model

[0004] In view of the deficiencies of the prior art, the utility model provides a main bearing of a wind turbine generator that improves the axial preloading force.

[0005] To achieve the above object, the technical solution of the utility model is as follows: A main bearing of a wind turbine generator includes a main shaft, a bearing arranged on the main shaft, and a gland. The bearing includes an outer ring and an inner ring. A placement groove for placing the inner ring is arranged on the main shaft. The outer surface of the gland on the side away from the main shaft is arranged in a circular arc shape, and its outer surface on the side facing the main shaft is parallel to the adjacent part of the main shaft. A gap is left between the gland on the side facing the main shaft and the main shaft. A abutting part is arranged on the gland corresponding to the position of the inner ring, and the upper edge of the abutting part is flush with the upper edge of the placement groove. Corresponding positions on the gland and the main shaft are provided with fixable holes that can be spliced, and the gland and the main shaft are fixed by passing a fixing member through the fixable holes.

[0006] The beneficial effects of the utility model are as follows: The gland with an outer surface arranged in a circular arc shape on the side away from the main shaft can better adapt to the slight deformation of the bearing seat or the shaft, and provide a more uniform contact pressure. The stress distribution generated by the circular arc-shaped gland during force application is more uniform, reducing the possibility of stress concentration, thereby improving the axial preloading effect of the bearing. The gap formed between the gland and the main shaft can allow the main shaft to thermally expand during operation without causing other components to be damaged due to excessive extrusion. In addition, the abutting part of the gland cooperates with the placement groove to provide axial preloading for the inner ring. At the same time, since the gland and the main shaft are fixed by fixing members, it can not only reduce the installation difficulty of the bearing but also, because the upper edge of the abutting part is flush with the upper edge of the placement groove, no other-direction pressing force will be generated during axial preloading, and thus will not affect the operation of the bearing.

[0007] Further, the bearing further includes two rows of rollers, there are two inner rings, there is one outer ring, rolling grooves are obliquely arranged on the inner rings corresponding to the rollers, anti-disengagement protrusions are arranged at both ends of the rolling grooves, and rolling surfaces are arranged on the outer ring corresponding to the number of rolling grooves and the rolling surfaces correspond to the rolling grooves so that the rollers can operate between the two.

[0008] The distance between the anti-disengagement protrusions at both ends of the rolling groove is slightly greater than the length of the roller, so as to ensure that the roller will not disengage from the inner ring on the premise of having a certain moving space. Secondly, two rows of rollers are arranged and the rollers are all obliquely arranged, so that the bearing can bear higher radial loads, improve the overall load-bearing capacity and optimize the spatial structure setting at the same time.

[0009] Further, an inner spacer is arranged between the two inner rings, both ends of the inner spacer are respectively abutted against the two inner rings, and the intersection of the two rolling surfaces corresponds to the center of the inner spacer.

[0010] In order to further optimize the performance of the bearing, an inner spacer is arranged between the two inner rings and both ends of the inner spacer are respectively abutted against the two inner rings, ensuring the correct gap between the inner rings and controlling the width of the inner rings, so as to further achieve the effect of optimizing the spatial structure. At the same time, this also helps to maintain the preload of the bearing, prevent mutual interference and friction between the inner rings, thereby improving the operating efficiency and service life of the bearing. At the same time, the intersection of the two rolling surfaces corresponds to the center of the inner spacer, and this precise alignment helps to ensure the stability of the bearing and reduce vibration.

[0011] Further, the fixing member is a fastening bolt, a retractable anti-loosening protrusion is arranged on the fixing member, a fastening hole is arranged in the fixing hole corresponding to the anti-loosening protrusion, the inner diameter of the fastening hole is larger than the inner diameter of the fixing hole, and the anti-loosening protrusion and the fastening hole are matched to form positioning.

[0012] First of all, the inner diameter of the fastening hole is larger than the inner diameter of the fixing hole, which provides enough space for the anti-loosening protrusion to achieve more precise positioning and more stable fixation. Secondly, the cooperation between the anti-loosening protrusion and the fastening hole not only enhances the axial positioning accuracy of the bearing, but also effectively prevents the bolt from loosening due to vibration or impact, thereby improving the connection stability between the main shaft and the gland.

[0013] Further, a receiving groove is arranged between the anti-loosening protrusion and the fixing member, and an elastic member with both ends respectively connected to the fixing member and the anti-loosening protrusion is arranged in the receiving groove, and the elastic member is used to make the anti-loosening protrusion tend to move in the direction away from the fixing member.

[0014] The use of the elastic member enables the anti-loosening protrusion to maintain a certain elastic deformation when subjected to vibration or impact, thereby maintaining the pre-tightening state of the bearing and enhancing the stability of the entire structure. Secondly, the addition of the elastic member provides additional damping to the system, which helps to absorb and reduce the impact caused by external vibration and protects the bearing from damage. In addition, the tendency of the elastic member to move backward, combined with the self-locking characteristic of the anti-loosening protrusion, enhances the self-locking function of the fixing member and effectively prevents the bolt from loosening. BRIEF DESCRIPTION OF THE DRAWINGS

[0015] Figure 1 is a cross-sectional view of an embodiment of the present invention;

[0016] Figure 2 is a cross-sectional view of the bearing of an embodiment of the present invention;

[0017] Figure 3 is a cross-sectional view of the gland of an embodiment of the present invention;

[0018] Figure 4 is a partially enlarged cross-sectional view at the abutting portion of an embodiment of the present invention;

[0019] Figure 5 is an axonometric view of the fixing member of an embodiment of the present invention;

[0020] Figure 6 is a cross-sectional view at the anti-loosening protrusion of the fixing member of an embodiment of the present invention;

[0021] Figure 7 is a partially enlarged cross-sectional view at the fixing hole of an embodiment of the present invention. DETAILED DESCRIPTION OF THE EMBODIMENTS

[0022] An embodiment of the main bearing of a wind turbine of the present invention is as Figures 1-7As shown in the figure, it includes a main shaft 1, a bearing 2 and a gland 3 arranged on the main shaft 1. The bearing 2 includes an outer ring 21 and two inner rings 22. An inner spacer 23 is arranged between the two inner rings 22, and abutting relationships are formed between the inner spacer 23 and the two inner rings 22 respectively. Two rows of rollers 25 sleeved in a cage 24 are arranged between the outer ring 21 and the inner rings 22. The parts of the outer ring 21 and the two inner rings 22 in contact with the rollers are rolling surfaces 211 and rolling grooves 221 respectively. Anti-disengagement protrusions 222 are arranged at both ends of the rolling groove 221 on the inner ring 22, and the linear distance formed by the connection of the two anti-disengagement protrusions 222 is greater than the length of the roller 25; the number of rolling surfaces 211 on the outer ring 21 corresponding to the rolling grooves 221 is set to 2. After the two rolling surfaces 211 are connected, their cross-section is V-shaped, and the center of the connection of the two rolling surfaces 211 corresponds to the center of the inner spacer 23, that is, the two are located on the same vertical straight line. A placement groove 11 for placing the inner spacer 23 and the two inner rings 22 is arranged on the main shaft 1, and one end of the placement groove 11 abuts against the side surface of one inner ring 22.

[0023] The outer surface of the gland 3 on the side facing away from the main shaft 1 is arranged in an arc shape. Its outer surface on the side facing the main shaft 1 is parallel to the adjacent part of the main shaft 1 and there is a gap for the thermal expansion of the main shaft 1 between it and the main shaft 1. An abutting portion 31 is arranged on the gland 1 at the position corresponding to the other inner ring 22. The abutting portion 31 cooperates with the placement groove 11 to form axial preloading of the two inner rings 22, and the upper edge of the abutting portion 31 is flush with the upper edge of the placement groove 11. A relief groove 311 for the thermal expansion gap of the inner ring 22 is left at the lower edge of the abutting portion 31.

[0024] Splicable fixing holes 5 are arranged at the corresponding positions of the gland 3 and the main shaft 1. The gland 3 and the main shaft 1 are fixed to each other by passing a fixing member 4 through the fixing holes 5. Since the fixing member 4 is a bolt, in order to prevent loosening between the fixing member 4 and the fixing holes 5 after the gland 3 and the main shaft 1 are connected, anti-loosening protrusions 43 are arranged on the fixing member 4, that is, a part of the spiral protrusions on the bolt is the anti-loosening protrusion 43. A receiving groove 41 for placing an elastic member 42 is arranged between the anti-loosening protrusion 43 and the fixing member 4. The elastic member 42 is a thrust spring and its two ends are respectively connected to the fixing member 4 and the anti-loosening protrusion 43. A fastening hole 51 corresponding to the anti-disengagement protrusion 222 is arranged in the fixing hole 5. The inner diameter of the fastening hole 51 is slightly larger than the inner diameter of the fixing hole 5, but less than half of the movement limit of the elastic member 42 pushing the anti-loosening protrusion 43, so that the anti-loosening protrusion 43 and the fastening hole 51 can effectively play a loosening prevention role after they are matched.

[0025] The installation process of this embodiment is as follows: Install the roller 25 into the cage 24, and then install the cage 24 into the inner ring 22. After placing the inner spacer 23 between the two inner rings 22, install the outer ring 21. After completing the assembly of the bearing 2, install the bearing 2 into the placement groove 11 of the main shaft 1 and make one side of the inner ring 22 abut against the placement groove 11. Subsequently, install the gland 3 and make the abutting portion 31 abut against the other side of the inner ring 22. Finally, insert the fixing member 4 into the fixing hole 5 for locking. During the process of locking the fixing member 4 into the fixing hole 5, the anti-loosening protrusion 43 is always compressed during the tightening process. After reaching the fastening hole 51, it is pushed by the elastic member 42 to cooperate and position with the fastening hole 51.

[0026] The above embodiments are only one of the preferred specific embodiments of the present invention. All common changes and substitutions made by those skilled in the art within the scope of the technical solution of the present invention are included in the protection scope of the present invention.

Claims

1. A main bearing of a wind turbine, comprising a main shaft, a bearing and a gland arranged on the main shaft, the bearing comprising an outer ring and an inner ring, and a placement groove for placing the inner ring being arranged on the main shaft, characterized in that: The outer surface of the gland on the side facing away from the main shaft is arranged in an arc shape, and the outer surface on the side facing the main shaft is parallel to the adjacent part of the main shaft. There is a gap between the gland and the main shaft on the side facing the main shaft; a abutting portion is provided on the gland corresponding to the position of the inner ring, and the upper edge of the abutting portion is flush with the upper edge of the placement groove; corresponding positions on the gland and the main shaft are provided with splicing fixing holes, and the gland and the main shaft are fixed by passing a fixing member through the fixing holes.

2. The main bearing of a wind turbine according to claim 1, wherein: The bearing further includes two rows of rollers, the number of inner rings is two, the number of outer rings is one, rolling grooves are obliquely arranged on the inner rings corresponding to the rollers, anti - detachment protrusions are arranged at both ends of the rolling grooves, and the outer ring is provided with rolling surfaces corresponding to the number of rolling grooves, and the rolling surfaces are opposite to the rolling grooves so that the rollers can operate between the two.

3. The main bearing of a wind turbine according to claim 2, characterized in that: An inner spacer is arranged between the two inner rings, both ends of the inner spacer abut against the two inner rings respectively, and the intersection of the two rolling surfaces corresponds to the center of the inner spacer.

4. The main bearing of a wind turbine according to claim 1, characterized in that: The fixing member is a fastening bolt, and a retractable anti - loosening protrusion is arranged on the fixing member. A fastening hole corresponding to the anti - loosening protrusion is arranged in the fixing hole. The inner diameter of the fastening hole is larger than the inner diameter of the fixing hole, and the anti - loosening protrusion and the fastening hole cooperate to form positioning.

5. The main bearing of a wind turbine according to claim 4, characterized in that: A receiving groove is arranged between the anti - loosening protrusion and the fixing member, and an elastic member with both ends respectively connected to the fixing member and the anti - loosening protrusion is arranged in the receiving groove. The elastic member is used to make the anti - loosening protrusion tend to move in a direction away from the fixing member.

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