Main shaft system of wind generating set and wind generating set

Abstract

The invention provides a main shaft system of a wind generating set and the wind generating set. The main shaft system comprises a first bearing seat and a second bearing seat which are separated from each other, the first bearing seat is provided with a first mounting hole, the second bearing seat is provided with a second mounting hole, and the first mounting hole and the second mounting hole are coaxially arranged; the main shaft is mounted in the first mounting hole and the second mounting hole, the first end of the main shaft is close to the first bearing seat and used for being connected with an impeller of the wind generating set, and the second end of the main shaft is close to the second bearing seat and used for being connected with a gearbox of the wind generating set; the first bearing assembly is arranged between the first bearing seat and the main shaft, the second bearing assembly is arranged between the second bearing seat and the main shaft, the first bearing assembly comprises a sliding bearing, and the second bearing assembly comprises a rolling bearing. According to the main shaft system, the stability of the output torque of the main shaft system can be improved.

Description

Technical Field

[0001] The present invention relates to the technical field of wind power generation, and particularly to a main shaft system of a wind turbine generator set and a wind turbine generator set. Background Art

[0002] The main shaft system of a wind turbine generator set is used to connect the impeller and the gearbox. The main shaft system includes a main shaft and front and rear bearings for supporting the main shaft.

[0003] Currently, the bearing arrangement in the main shaft system generally adopts a pure sliding shaft system or a pure rolling shaft system.

[0004] The rolling shaft system has a complex structure and high cost. And as the power of the wind turbine generator set continuously increases, the size of the rolling bearings is large, further increasing the use cost of the rolling bearings. The sliding shaft system has a large gap, resulting in a relatively serious eccentric alignment problem, which makes the torque stability received by the gearbox poor and has an adverse impact on the gearbox. The sliding shaft system also has the problem of unstable low-speed start, which will accelerate the wear of the bearing bush of the sliding bearing. In addition, the sliding shaft system also has an axial crosstalk problem, and the rear sliding bearing is not convenient to replace and generally needs to be replaced in cooperation with an axial thrust bearing.

[0005] In addition, as the capacity of the wind turbine generator set gradually increases, higher requirements are put forward for the torque stability of the main shaft system input to the gearbox. Summary of the Invention

[0006] An object of the present invention is to solve at least one of the above problems.

[0007] Another object of the present invention is to reduce the wear caused by eccentricity.

[0008] Another object of the present invention is to improve the problem of unstable low-speed start.

[0009] Another object of the present invention is to improve the axial crosstalk problem of the main shaft.

[0010] Another object of the present invention is to improve the torque stability of the main shaft system input to the gearbox.

[0011] Another object of the present invention is to reduce the assembly process, lower the cost, and reduce the assembly error.

[0012] According to one aspect of the present invention, there is provided a main shaft system of a wind turbine generator set, the main shaft system comprising: a first bearing housing and a second bearing housing separated from each other, the first bearing housing having a first mounting hole, the second bearing housing having a second mounting hole, the first mounting hole and the second mounting hole being coaxially arranged; a main shaft mounted in the first mounting hole and the second mounting hole, a first end of the main shaft being close to the first bearing housing and adapted to be connected to an impeller of the wind turbine generator set, a second end of the main shaft being close to the second bearing housing and adapted to be connected to a gearbox of the wind turbine generator set; a first bearing assembly and a second bearing assembly, the first bearing assembly being disposed between the first bearing housing and the main shaft, the second bearing assembly being disposed between the second bearing housing and the main shaft, wherein the first bearing assembly includes a sliding bearing and the second bearing assembly includes a rolling bearing.

[0013] Optionally, the second bearing housing is integrally formed with an outer gear ring of the gearbox.

[0014] Optionally, the first bearing assembly includes a plurality of sliding bearings circumferentially distributed along the main shaft.

[0015] Optionally, each of the sliding bearings includes a support substrate, a bearing bush assembly, and an adjustment assembly connecting the support substrate and the bearing bush assembly, the adjustment assembly being capable of moving the bearing bush assembly relative to the support substrate in the axial and radial directions of the support substrate and capable of adjusting the inclination angle of the bearing bush assembly relative to the support substrate.

[0016] Optionally, the rolling bearing is a tapered roller bearing, and the tapered roller bearing includes an outer ring, an inner ring, and tapered rollers disposed between the outer ring and the inner ring.

[0017] Optionally, from the first end to the second end of the main shaft, the inclination direction of the rotation axis of the tapered rollers relative to the axis of the main shaft is opposite to the inclination direction of the bearing bush surface of the sliding bearing relative to the axis of the main shaft.

[0018] Optionally, from the first end to the second end of the main shaft, the bearing bush surface of the sliding bearing is inclined in a direction away from the axis of the main shaft, and the rotation axis of the tapered rollers is inclined in a direction close to the axis of the main shaft.

[0019] Optionally, from the first end to the second end of the main shaft, the bearing bush surface of the sliding bearing is inclined in a direction close to the axis of the main shaft, and the rotation axis of the tapered rollers is inclined in a direction away from the axis of the main shaft.

[0020] Optionally, the number of the sliding bearings located below the center line of the main shaft is greater than the number of the sliding bearings located above the center line of the main shaft.

[0021] According to another aspect of the present invention, there is provided a wind turbine generator, which includes the main shaft system as described above.

[0022] According to the present invention, the main shaft system adopts the configuration of sliding bearings and rolling bearings, which improves the load-bearing capacity, extends the service life, can improve the stability of the output torque of the main shaft system, reduces the damage to the gearbox, and can also solve the centering problem with the gearbox.

[0023] According to the present invention, the first bearing housing and the second bearing housing of the main shaft system are designed separately, which can improve the design freedom and reduce the material cost.

[0024] According to the present invention, the second bearing housing in the main shaft system and the outer gear ring of the gearbox are integrally designed, which can eliminate the assembly process, reduce the number of bolts used, thereby reducing the cost, and can also reduce the cumulative assembly error.

[0025] According to the present invention, the sliding bearings and the rolling bearings in the main shaft system are arranged face to face or back to back, which reduces the axial end play and improves the stability of the output torque at the output end.

[0026] According to the present invention, the sliding bearing can realize the axial, radial and tilt angle adjustment of the bearing bush assembly.

[0027] According to the present invention, the sliding bearing can reduce the wear caused by eccentricity, improve the problem of unstable low-speed start, and improve the stability of the output torque. BRIEF DESCRIPTION OF THE DRAWINGS

[0028] Through the following detailed description in conjunction with the drawings, the above and other objects, features and advantages of the present invention will become clearer, wherein:

[0029] Figure 1 is a perspective view of the main shaft system according to an embodiment of the present invention;

[0030] Figure 2 is Figure 1 a structural diagram of the integral design of the second bearing housing and the outer gear ring of the gearbox in

[0031] Figure 3 is Figure 1 an axial sectional view of the main shaft system taken along the A-A line of

[0032] Figure 4 is Figure 1 an axial sectional view of the main shaft system taken along the B-B line of

[0033] Figure 5And Figure 6 are perspective views of a sliding bearing viewed from different directions;

[0034] Figure 7 is a sectional view of the sliding bearing taken along the C-C line of Figure 5 .

[0035] Explanation of reference numerals in the drawings: 10 - bearing housing, 100 - sliding bearing, 11 - first bearing housing, 110 - support substrate, 111 - stop projection, 112 - limiting member, 11a - first mounting hole, 11b - first stop portion, 12 - second bearing housing, 120 - bearing bush assembly, 120a - bearing bush surface, 121 - bearing bush body, 122 - first swing arm, 123 - second swing arm, 12a - second mounting hole, 12b - third stop portion, 130 - axial adjustment device, 131 - sliding body, 132 - first protrusion, 133 - second protrusion, 134 - driving device, 140 - first radial adjustment device, 141 - first moving body, 142 - first swing arm connecting member, 143 - first lifting device, 150 - second radial adjustment device, 151 - second moving body, 152 - second swing arm connecting member, 153 - second lifting device, 161 - front-end oil pressure sensor, 162 - rear-end oil pressure sensor, 170 - rotational speed sensor, 200 - tapered roller bearing, 210 - outer ring, 220 - inner ring, 230 - tapered roller, 30 - external gear ring, 40 - main shaft, 41 - first end, 42 - second end, 43 - second stop portion. Detailed Description of the Preferred Embodiment

[0036] Hereinafter, the technical solutions in the embodiments of the present invention will be clearly and completely described with reference to the accompanying drawings in the embodiments of the present invention. Apparently, the described embodiments are only a part of the embodiments of the present invention, rather than all of the embodiments. All other embodiments obtained by those of ordinary skill in the art based on the embodiments of the present invention without creative efforts shall fall within the protection scope of the present invention.

[0037] Unless otherwise defined, all technical and scientific terms used herein have the same meaning as commonly understood by those of ordinary skill in the art. The terms used in the specification of the present invention are only for the purpose of describing specific embodiments, and are not intended to limit the present invention.

[0038] Hereinafter, a main shaft system and a sliding bearing according to an embodiment of the present invention will be described in detail with reference to Figures 1 to 7 .

[0039] Figure 1 is a perspective view of a main shaft system according to an embodiment of the present invention. Figure 2 is Figure 1 a structural diagram of an integrated design of the second bearing housing and the external gear ring of the gearbox in Figure 3is the axial sectional view of the main shaft system taken along the Figure 1 A-A line of Figure 4 is the axial sectional view of the main shaft system taken along the Figure 1 B-B line of Figure 5 and Figure 6 are the three-dimensional views of the sliding bearing seen from different directions. Figure 7 is the sectional view of the sliding bearing taken along the Figure 5 C-C line of

[0040] Main shaft system of a wind turbine generator

[0041] As Figure 1 shown, the main shaft system according to an embodiment of the present invention includes a bearing housing 10 and a main shaft 40. The bearing housing 10 has a mounting hole, and the main shaft 40 is mounted in the mounting hole of the bearing housing 10. The first end 41 of the main shaft 40 is close to the first bearing housing 11 and is used for connecting with the impeller of the wind turbine generator set, and the second end 42 of the main shaft 40 is close to the second bearing housing 12 and is used for connecting with the gearbox of the wind turbine generator set.

[0042] The main shaft system according to an embodiment of the present invention may further include a first bearing assembly and a second bearing assembly. The first bearing assembly may be disposed between the bearing housing 10 and the outer peripheral surface of the first end 41 of the main shaft 40, and the second bearing assembly may be disposed between the bearing housing 10 and the outer peripheral surface of the second end 42 of the main shaft 40.

[0043] According to an embodiment of the present invention, the first bearing assembly includes a sliding bearing 100, and the second bearing assembly includes a rolling bearing. Considering the overall mechanical properties of the main shaft system, the first bearing assembly is close to the hub blade of the wind turbine generator set and needs to bear the weight of the hub blade and the alternating load brought by the wind load. It not only bears the alternating load, but also bears a large load and is easily damaged. According to an embodiment of the present invention, the first bearing assembly may include a sliding bearing 100. The sliding bearing has a large load-bearing capacity, so the load-bearing capacity of the first bearing assembly can be improved and the service life can be extended. In addition, the sliding bearing 100 is located at the front end of the main shaft system, which is convenient for replacement. The second bearing assembly is close to the gearbox of the wind turbine generator set, with relatively less damage but needs to be able to stably output torque to reduce the damage to the gearbox. According to an embodiment of the present invention, the second bearing assembly includes a rolling bearing. The rolling bearing outputs torque more stably, so the stability of the torque output by the main shaft system can be improved, the damage to the gearbox can be reduced, and at the same time, the centering problem with the gearbox can be solved.

[0044] According to an embodiment of the present invention, as Figure 1As shown, the bearing housing 10 may include a first bearing housing 11 and a second bearing housing 12 that are separated from each other. The first bearing housing 11 has a first mounting hole 11a, and the second bearing housing 12 has a second mounting hole 12a. The first mounting hole 11a and the second mounting hole 12a are coaxially arranged. The main shaft 40 is installed in the first mounting hole 11a and the second mounting hole 12a. According to an embodiment of the present invention, the first bearing housing 11 and the second bearing housing 12 are of a split design, which can improve the design freedom of the first bearing housing 11 and the second bearing housing 12 and can save material costs.

[0045] According to an embodiment of the present invention, as Figure 2 shown, the second bearing housing 12 may be integrally formed with the outer gear ring 30 of the gearbox. The integrated design of the second bearing housing 12 and the outer gear ring 30 of the gearbox can better ensure the stability of the torque input from the main shaft system to the gearbox end and reduce the damage to the internal components of the gearbox. In addition, the integrated design of the second bearing housing 12 and the outer gear ring 30 of the gearbox can eliminate the assembly process, reduce the number of bolts used, thereby reducing costs. In addition, it can also reduce the cumulative assembly error.

[0046] Figures 1 to 3 The case where the diameter of the outer peripheral surface of the outer gear ring 30 of the gearbox is greater than the diameter of the outer peripheral surface of the second bearing housing 12 is shown in

[0047] According to an embodiment of the present invention, as Figure 4 shown, the first bearing assembly includes a plurality of sliding bearings 100 distributed circumferentially along the main shaft 40. The first bearing assembly includes a plurality of distributed sliding bearings 100. The distributed design makes the assembly convenient and enables on-tower maintenance, avoiding the risks and costs of going down the tower.

[0048] As Figure 3 and Figure 4 shown, the plurality of sliding bearings 100 may be arranged at the gap between the first bearing housing 11 and the main shaft 40. Since the sliding bearings 100 located below the center line of the main shaft 40 need to support the weight of the main shaft 40, the number of sliding bearings 100 located below the center line of the main shaft 40 is greater than the number of sliding bearings 100 located above the center line of the main shaft 40. In addition, a sliding bearing 100 may be provided directly below the main shaft 40. The distribution density of the sliding bearings 100 below the center line of the main shaft 40 may also be greater than the distribution density of the sliding bearings 100 above the center line of the main shaft 40.

[0049] As Figure 3As shown, a first stop portion 11b may be provided on the first bearing seat 11, and the sliding bearing 100 may have a stop protrusion 111. The first stop portion 11b and the stop protrusion 111 protrude to limit the position of the sliding bearing 100.

[0050] According to an embodiment of the present invention, as Figure 5 shown, the sliding bearing 100 may include a support substrate 110, a bearing bush assembly 120, and an adjustment assembly connecting the support substrate 110 and the bearing bush assembly 120. The adjustment assembly can enable the bearing bush assembly 120 to move axially and radially relative to the support substrate 110 along the axis of the support substrate 110 and adjust the inclination angle of the bearing bush surface 120a relative to the support substrate 110.

[0051] According to the present invention, by enabling the bearing bush assembly 120 to move axially and radially relative to the support substrate 110 along the axis of the support substrate 110 and adjusting the inclination angle of the bearing bush assembly 120 relative to the support substrate 110, the installation and replacement of the sliding bearing 100 can be easily achieved. The structure of the sliding bearing 100 will be described in detail later.

[0052] According to an embodiment of the present invention, as Figure 3 shown, the rolling bearing included in the second bearing assembly is a tapered roller bearing 200. The tapered roller bearing 200 may include an outer ring 210, an inner ring 220, and tapered rollers 230 provided between the outer ring 210 and the inner ring 220. According to an embodiment of the present invention, the second bearing seat 12 separated from the first bearing seat 11 is integrated with the external gear ring 30 of the gearbox, and the rolling bearing uses a tapered roller bearing, which can better ensure the stability of the torque input from the main shaft system to the gearbox end and reduce the damage to the internal components of the gearbox.

[0053] According to an embodiment of the present invention, as Figure 3 shown, a second stop portion 43 may be provided on the main shaft 40, and a third stop portion 12b may be provided on the second bearing seat 12. The outer ring 210 and the inner ring 220 of the tapered roller bearing 200 can be limited by the third stop portion 12b and the second stop portion 43 respectively.

[0054] According to an embodiment of the present invention, as Figure 3 shown, from the first end 41 to the second end 42 of the main shaft 40, the inclination direction of the rotation axis R of the tapered rollers 230 relative to the axis L of the main shaft 40 is opposite to the inclination direction of the bearing bush surface 120a of the sliding bearing 100 relative to the axis L of the main shaft 40.

[0055] As an example, as Figure 3As shown, from the first end 41 to the second end 42 of the main shaft 40, the bearing surface 120a of the sliding bearing 100 is inclined in a direction away from the axis L of the main shaft 40, and the rotation axis of the tapered roller 230 is inclined in a direction close to the axis L of the main shaft 40. That is, the sliding bearing 100 and the tapered roller bearing 200 are arranged face to face. The axial components of the loads borne by the sliding bearing 100 and the tapered roller bearing 200 arranged face to face are in opposite directions to each other. Specifically, the axial component of the sliding bearing 100 points towards the tapered roller bearing 200 side, and the axial component of the tapered roller bearing 200 points towards the sliding bearing 100 side. Therefore, the axial components of the loads borne by the sliding bearing 100 and the tapered roller bearing 200 can cancel each other out, thereby preventing the axial movement of the main shaft 40 and improving the stability of the output torque.

[0056] However, the present invention is not limited to this. The sliding bearing 100 can also be arranged back to back with the tapered roller bearing 200. In this case, from the first end 41 to the second end 42 of the main shaft 40, the bearing surface 120a of the sliding bearing 100 is inclined in a direction close to the axis L of the main shaft 40 (i.e., opposite to the Figure 3 inclination direction), and the rotation axis of the tapered roller 230 is inclined in a direction away from the axis L of the main shaft 40 (i.e., opposite to the Figure 3 inclination direction).

[0057] The axial components of the loads borne by the sliding bearing 100 and the tapered roller bearing 200 arranged back to back are in opposite directions to each other. Specifically, the axial component of the sliding bearing 100 points towards the side away from the tapered roller bearing 200, and the axial component of the tapered roller bearing 200 points towards the side away from the sliding bearing 100. In this case, the axial components of the loads borne by the sliding bearing 100 and the tapered roller bearing 200 can also cancel each other out, thereby preventing the axial movement of the main shaft 40 and improving the stability of the output torque.

[0058] Slipper bearing

[0059] Hereinafter, the sliding bearing according to an embodiment of the present invention will be described in detail. As Figure 4 shown, the sliding bearing 100 according to an embodiment of the present invention can adopt a distributed design.

[0060] As Figure 5As shown, each sliding bearing 100 may include a support substrate 110, a bearing bush assembly 120, and an adjustment assembly connecting the support substrate 110 and the bearing bush assembly 120. The outer peripheral surface of the support substrate 110 is arc-shaped for abutting against the first bearing housing 11. The bearing bush assembly 120 may be disposed radially inside the support substrate 110 and spaced apart from the support substrate 110. The bearing bush surface 120a of the bearing bush assembly 120 is arc-shaped to fit against the outer peripheral surface of the main shaft 40 and support the main shaft 40 in a specific operating mode (e.g., shutdown state). The adjustment assembly according to an embodiment of the present invention can adjust the spacing between the bearing bush assembly 120 and the support substrate 110 and adjust the inclination angle of the bearing bush assembly 120 relative to the support substrate 110, thereby facilitating the support of the main shaft 40 during shutdown or forming a favorable oil film between the bearing bush surface 120a and the main shaft 40 after startup.

[0061] As Figures 5 to 7 shown, according to an embodiment of the present invention, the adjustment assembly may include an axial adjustment device 130 and a radial adjustment device.

[0062] The axial adjustment device 130 may be disposed radially inside the support substrate 110 and is capable of moving along the axial direction of the support substrate 110 (i.e., Figure 7 the left-right direction in Figure 3 and Figure 7 shown) on the support substrate 110. When the axial adjustment device 130 moves along the axial direction of the support substrate 110 towards Figure 7 the left side of Figure 7 it, the spacing between the bearing bush surface 120a and the main shaft 40 increases; when the axial adjustment device 130 moves along the axial direction of the support substrate 110 towards Figure 7 the right side of Figure 7 it, the spacing between the bearing bush surface 120a and the main shaft 40 decreases. According to an embodiment of the present invention, the radial adjustment device can move the bearing bush assembly 120 relative to the support substrate 110 along the radial direction of the support substrate 110 (i.e., Figure 7 the up-down direction in Figure 7 shown) and can swing the bearing bush assembly 120 around the chordal direction of the support substrate 110 (i.e., Figure 7 the direction perpendicular to the paper surface in

[0063] shown). The chordal direction of the support substrate 110 is perpendicular to the radial and axial directions of the support substrate 110. When the radial adjustment device moves the bearing bush assembly 120 relative to the support substrate 110 along the radial direction of the support substrate 110, the spacing between the bearing bush surface 120a and the main shaft 40 can also be increased or decreased. When the radial adjustment device swings the bearing bush assembly 120 around the chordal direction of the support substrate 110, the inclination angle of the bearing bush surface 120a relative to the support substrate 110 can be adjusted, thereby adjusting the spacing between the front end and the rear end of the bearing bush surface 120a and the main shaft 40.

[0064] According to an embodiment of the present invention, as Figures 5 to 7As shown, the radial adjustment device may include a first radial adjustment device 140 and a second radial adjustment device 150. The first ends of the first radial adjustment device 140 and the second radial adjustment device 150 are connected to the axial adjustment device 130 and can move radially along the support substrate 110. The bearing shell assembly 120 is swingably connected to the second ends 42 of the first radial adjustment device 140 and the second radial adjustment device 150 around the chordal direction of the support substrate 110. When the first radial adjustment device 140 and the second radial adjustment device 150 move radially along the support substrate 110 simultaneously, the distance between the bearing shell surface 120a and the main shaft 40 can be increased or decreased. When one of the first radial adjustment device 140 and the second radial adjustment device 150 moves radially along the support substrate 110, the inclination angle of the bearing shell surface 120a relative to the support substrate 110 can be increased or decreased.

[0065] According to an embodiment of the present invention, as Figures 5 to 7 shown, the axial adjustment device 130 may include a sliding body 131, and a first protrusion 132 and a second protrusion 133 extending radially from the sliding body 131 along the support substrate 110 towards the bearing shell assembly 120. The support substrate 110 may include a limiting member 112 that limits the axial movement range of the sliding body 131. For example, a groove may be provided on the inner circumferential surface of the support substrate 110, at least a part of the sliding body 131 is disposed in the groove and can slide axially in the groove along the support substrate 110, and the groove wall of the groove can be used as the limiting member 112. The axial adjustment device 130 may further include a driving device 134 that drives the sliding body 131 to move axially along the support substrate 110 relative to the support substrate 110. The specific type of the driving device 134 is not limited. For example, it can be a hydraulic, stepper motor, or other driving device.

[0066] According to an embodiment of the present invention, as Figures 5 to 7 shown, the first radial adjustment device 140 may be connected to the first protrusion 132 and can move radially relative to the first protrusion 132 along the support substrate 110, and the second radial adjustment device 150 may be connected to the second protrusion 133 and can move radially relative to the second protrusion 133 along the support substrate 110.

[0067] The first radial adjustment device 140 may include a first moving body 141. The first moving body 141 is sleeved outside the first protrusion 132, a first cavity is formed inside the first protrusion 132 and the first moving body 141, and the first radial adjustment device 140 further includes a first lifting device 143 disposed in the first cavity, and the first lifting device 143 is used to drive the first moving body 141 to move radially relative to the first protrusion 132 along the support substrate 110. The first lifting device 143 can be, for example, a hydraulic, stepper motor, or other driving device, but the present invention is not limited thereto.

[0068] The second radial adjustment device 150 includes a second moving body 151. The second moving body 151 is sleeved outside the second protruding portion 133. A second cavity is formed in the second protruding portion 133 and the second moving body 151. The second radial adjustment device 150 further includes a second lifting device 153 disposed in the second cavity. The second lifting device 153 is configured to drive the second moving body 151 to move radially relative to the second protruding portion 133 along the support substrate 110. The second lifting device 153 may be a driving device such as a hydraulic pressure or a stepper motor. However, the present invention is not limited thereto.

[0069] As Figures 5 to 7 shown, the bearing shell assembly 120 may include a bearing shell main body 121, and a first swing arm 122 and a second swing arm 123 that protrude from the radial outer side of the bearing shell main body 121 and are spaced apart from each other. The first swing arm 122 and the second swing arm 123 may be swingably connected to the second end of the first radial adjustment device 140 and the second end of the second radial adjustment device 150 respectively around the chord direction of the support substrate 110.

[0070] Specifically, the first radial adjustment device 140 may further include a pair of first swing arm connectors 142 that protrude radially from the first moving body 141 toward the support substrate 110 and are spaced apart from each other along the chord direction of the support substrate 110. The second radial adjustment device 150 may further include a pair of second swing arm connectors 152 that protrude radially from the second moving body 151 toward the support substrate 110 and are spaced apart from each other along the chord direction of the support substrate 110. The first swing arm 122 may be swingably connected to a pair of first swing arm connectors 142 located on both sides of the first swing arm 122 through a rotating shaft. The second swing arm 123 may be swingably connected to a pair of second swing arm connectors 152 located on both sides of the second swing arm 123 through a rotating shaft.

[0071] Hereinafter, the working principle of the sliding bearing 100 according to the embodiment of the present invention will be described in detail.

[0072] According to an embodiment of the present invention, the main shaft system may further include a front-end oil pressure sensor 161 for sensing the oil pressure (i.e., the oil film pressure therebetween) between the front axial end of the bearing shell surface 120a and the main shaft 40, a rear-end oil pressure sensor 162 for sensing the oil pressure between the rear axial end of the bearing shell surface 120a and the main shaft 40, and a rotational speed sensor 170 for sensing the rotational speed of the main shaft 40.

[0073] As Figure 7As shown, the front oil pressure sensor 161 can be disposed at the axial front end of the bearing surface 120a of the sliding bearing 100, and the rear oil pressure sensor 162 can be disposed at the axial rear end of the bearing surface 120a of the sliding bearing 100. The rotational speed sensor 170 can be disposed on the front end side of the bearing body 121. However, the specific installation positions of the front oil pressure sensor 161, the rear oil pressure sensor 162, and the rotational speed sensor 170 are not limited as long as the above-mentioned measurement functions can be achieved. For example, they can also be installed on the main shaft 40.

[0074] According to an embodiment of the present invention, the adjusting assembly of the sliding bearing 100 can adjust the distance between the bearing surface 120a of the bearing assembly 120 and the main shaft 40 and the inclination angle of the bearing surface 120a of the bearing assembly 120 relative to the support substrate 110 according to the oil pressure sensed by the front oil pressure sensor 161 and the rear oil pressure sensor 162 and the rotational speed sensed by the rotational speed sensor 170. Hereinafter, the operation modes of the axial adjusting device 130 and the radial adjusting device will be described according to the rotational speed sensed by the rotational speed sensor 170.

[0075] The rotational speed sensed by the rotational speed sensor 170 is less than the predetermined rotational speed

[0076] According to an embodiment of the present invention, when the rotational speed sensed by the rotational speed sensor 170 is less than a predetermined rotational speed, the first radial adjusting device 140 and the second radial adjusting device 150 can move radially along the support substrate 110 according to the average oil pressure of the oil pressure sensed by the front oil pressure sensor 161 and the oil pressure sensed by the rear oil pressure sensor 162 (when the front oil pressure sensor 161 and the rear oil pressure sensor 162 are provided in plurality, this average oil pressure is the average oil pressure of the oil pressures sensed by all the oil pressure sensors) to adjust the distance between the bearing surface 120a and the main shaft 40.

[0077] That is to say, when the rotational speed sensed by the rotational speed sensor 170 is less than the predetermined rotational speed, the distance between the bearing surface 120a and the main shaft 40 can be adjusted by using the first radial adjusting device 140 and the second radial adjusting device 150. The specific value of the predetermined rotational speed is not limited and can be determined according to the power of the wind turbine generator set. When the rotational speed of the main shaft 40 is less than the predetermined rotational speed, the wind turbine generator set may not be able to meet the power generation requirements, so it is necessary to stop the machine. As an example, the predetermined rotational speed can be 5 revolutions per minute.

[0078] When designing the main shaft system, the optimal matching oil pressure is designed for each rotational speed. According to an embodiment of the present invention, when the rotational speed sensed by the rotational speed sensor 170 is less than a predetermined rotational speed, if the average oil pressure is greater than the designed oil pressure matching the measured rotational speed, the first radial adjustment device 140 and the second radial adjustment device 150 move radially along the support substrate 110 (for example, the first radial adjustment device 140 and the second radial adjustment device 150 move toward the side close to the support substrate 110) to increase the distance between the bearing surface 120a and the main shaft 40; if the average oil pressure is less than the designed oil pressure matching the measured rotational speed, the first radial adjustment device 140 and the second radial adjustment device 150 move radially along the support substrate 110 (for example, the first radial adjustment device 140 and the second radial adjustment device 150 move toward the side away from the support substrate 110) to decrease the distance between the bearing surface 120a and the main shaft 40.

[0079] When the rotational speed sensed by the rotational speed sensor 170 is zero, the first radial adjustment device 140 and the second radial adjustment device 150 move radially along the support substrate 110 to make the bearing surface 120a of the bearing assembly 120 fit with the main shaft 40. This state may correspond to the unit shutdown stage. At this time, there is no oil film between the bearing surface 120a and the main shaft 40. The first radial adjustment device 140 and the second radial adjustment device 150 cooperate to adjust so that the bearing surface 120a fits with the main shaft 40 to support the main shaft 40. At this time, the main shaft 40 is coaxial with the first bearing seat 11, the second bearing seat 12, and the gearbox to reduce unnecessary wear caused by eccentricity and damage to the bearing surface 120a.

[0080] When the unit is just starting up (at this time the rotational speed is less than the predetermined rotational speed), as the rotational speed increases, an oil film begins to form between the main shaft 40 and the bearing surface 120a. The first radial adjustment device 140 and the second radial adjustment device 150 make the bearing surface 120a start to have a gap with the outer peripheral surface of the main shaft 40 according to the above-mentioned average oil pressure to facilitate the formation of the oil film. In addition, since the sliding bearing 100 of the present invention adjusts the main shaft 40 to be coaxial with the first bearing seat 11, the second bearing seat 12, and the gearbox when not started (rotational speed is zero), it can still better ensure their coaxiality during the process of slowly forming a gap and then forming an oil film, preventing the main shaft 40 from shaking unstably due to non-coaxiality and improving the problem of unstable main shaft during low-speed startup of the unit.

[0081] In addition, when the unit is about to shut down (at this time the rotational speed is less than the predetermined rotational speed), as the rotational speed decreases, the first radial adjustment device 140 and the second radial adjustment device 150 adjust the gap between the bearing surface 120a and the main shaft 40 according to the rotational speed matching oil pressure until shutdown.

[0082] During the above adjustment process, when the oil pressure difference between the oil pressure sensed by the front-end oil pressure sensor 161 (when multiple front-end oil pressure sensors 161 are provided, this oil pressure can be the average oil pressure sensed by all front-end oil pressure sensors) and the oil pressure sensed by the rear-end oil pressure sensor 162 (when multiple rear-end oil pressure sensors 162 are provided, this average oil pressure is the average oil pressure sensed by all oil pressure sensors) is greater than a predetermined value, the first radial adjustment device 140 or the second radial adjustment device 150 moves radially along the support substrate 110 to reduce the oil pressure difference.

[0083] That is to say, by moving the first radial adjustment device 140 or the second radial adjustment device 150 radially along the support substrate 110, the inclination angle between the bearing bush surface 120a and the support substrate 110 can be adjusted, the oil pressure difference can be reduced (for example, reduced to 0), the coaxiality of the main shaft 40 with the first bearing block 11 and the second bearing block 12 can be improved, and the stability of the output torque can be improved. When the oil pressure difference is 0 and there is no fluctuation, it means that the main shaft 40 is coaxial with the first bearing block 11, the second bearing block 12 and the gearbox.

[0084] The rotational speed sensed by the rotational speed sensor 170 is greater than or equal to the predetermined rotational speed and less than or equal to the full-load rotational speed

[0085] According to an embodiment of the present invention, when the rotational speed sensed by the rotational speed sensor 170 is greater than or equal to a predetermined rotational speed and less than or equal to the full-load rotational speed, the axial adjustment device 130 can move axially along the support substrate 110 according to the average oil pressure of the oil pressure sensed by the front-end oil pressure sensor 161 and the oil pressure sensed by the rear-end oil pressure sensor 162 (when multiple front-end oil pressure sensors 161 and multiple rear-end oil pressure sensors 162 are provided, this average oil pressure is the average oil pressure sensed by all oil pressure sensors) to adjust the distance between the bearing bush surface 120a of the bearing bush assembly 120 and the main shaft 40.

[0086] That is to say, when the rotational speed of the main shaft 40 is greater than or equal to a predetermined rotational speed and less than or equal to the full-load rotational speed, the axial adjustment device 130 can be used to adjust the distance between the bearing bush surface 120a of the bearing bush assembly 120 and the main shaft 40. The predetermined rotational speed is the same as the above concept and will not be described repeatedly here. The full-load rotational speed is the rotational speed at full load, and the specific value is not limited and can be determined according to the power of the wind turbine generator set.

[0087] According to an embodiment of the present invention, when the rotational speed sensed by the rotational speed sensor 170 is greater than or equal to a predetermined rotational speed and less than or equal to the full-load rotational speed, when the average oil pressure is greater than the designed oil pressure matched with the measured rotational speed, the axial adjustment device 130 moves axially along the support substrate 110 (for example, towards Figure 7The left movement in) increases the spacing between the bearing shell assembly 120 and the main shaft 40; when the average oil pressure is less than the designed oil pressure matching the measured rotational speed, the axial adjustment device 130 moves axially along the support substrate 110 (e.g., towards Figure 7 the right movement in) to reduce the spacing between the bearing shell assembly 120 and the main shaft 40.

[0088] When the average oil pressure is greater than the designed oil pressure, it is necessary to increase the spacing between the bearing shell surface 120a and the main shaft 40 through the axial adjustment device 130, thereby increasing the oil film thickness between the bearing shell surface 120a and the main shaft 40, and further reducing the oil pressure; when the average oil pressure is less than the designed oil pressure, it is necessary to appropriately increase the oil pressure by reducing the spacing between the bearing shell surface 120a and the main shaft 40 through the axial adjustment device 130 to ensure the stability of the shafting. That is to say, the axial adjustment device 130 will adjust according to the recommended optimal rotational speed matching oil pressure to make the sliding bearing 100 in the best sliding state.

[0089] During the rotational speed increase process after the unit starts (the rotational speed increases to be greater than or equal to the predetermined rotational speed), the above-mentioned adjustment can be carried out through the axial adjustment device 130 according to the sensed rotational speed and average oil pressure to facilitate the formation of the oil film.

[0090] During the rotational speed stabilization process (e.g., at this time the rotational speed is the full-load rotational speed), the above-mentioned adjustment can be carried out through the axial adjustment device 130 according to the sensed rotational speed and average oil pressure to make the sliding bearing in the best sliding state.

[0091] In addition, during the rotational speed decrease process and the process of the rotational speed fluctuating up and down, as long as the sensed rotational speed is greater than or equal to the predetermined rotational speed and less than or equal to the full-load rotational speed, the above-mentioned adjustment can be carried out through the axial adjustment device 130 according to the sensed rotational speed and average oil pressure.

[0092] During the above adjustment process, when the oil pressure sensed by the front-end oil pressure sensor 161 (when multiple front-end oil pressure sensors 161 are provided, this oil pressure can be the average oil pressure sensed by all front-end oil pressure sensors) and the oil pressure sensed by the rear-end oil pressure sensor 162 (when multiple rear-end oil pressure sensors 162 are provided, this average oil pressure is the average oil pressure sensed by all oil pressure sensors) have an oil pressure difference greater than a predetermined value (the specific magnitude of the predetermined value is not limited, for example, it can be determined according to the output torque requirement of the main shaft system), the first radial adjustment device 140 or the second radial adjustment device 150 moves radially along the support substrate 110 to reduce the oil pressure difference. That is to say, by the radial movement of the first radial adjustment device 140 or the second radial adjustment device 150 along the support substrate 110, the inclination angle between the bearing bush surface 120a and the support substrate 110 can be adjusted, the oil pressure difference can be reduced (for example, reduced to 0), the coaxiality of the main shaft 40 with the first bearing block 11 and the second bearing block 12 can be improved, and the stability of the output torque can be improved. When the oil pressure difference is 0 and there is no fluctuation, it indicates that the main shaft 40 is coaxial with the first bearing block 11, the second bearing block 12, and the gearbox.

[0093] In addition, when the sliding bearing 100 needs to be replaced, the distance between the bearing bush surface 120a and the support substrate 110 and the inclination angle of the bearing bush surface 120a relative to the support substrate 110 can be adjusted through the first radial adjustment device 140 and the second radial adjustment device 150 to disassemble the sliding bearing 100. The installation process is similar, that is, the sliding bearing 100 is pushed between the first bearing block 11 and the main shaft 40 by adjusting the distance between the bearing bush surface 120a and the support substrate 110 and the inclination angle of the bearing bush surface 120a relative to the support substrate 110.

[0094] It can be seen from the above analysis that the sliding bearing according to the present invention can reduce the wear caused by eccentricity, improve the problem of unstable low-speed start, and improve the stability of the output torque.

[0095] Wind turbine generator

[0096] According to an embodiment of the present invention, a wind turbine generator including the main shaft system as described above can also be provided.

[0097] The sliding bearing and the main shaft system according to the present invention can achieve beneficial technical effects not limited to the following description.

[0098] The main shaft system adopts a configuration of a sliding bearing and a rolling bearing, which improves the load-bearing capacity, extends the service life, can improve the stability of the output torque of the main shaft system, reduce the damage to the gearbox, and at the same time can also solve the alignment problem with the gearbox.

[0099] The split design of the first bearing block and the second bearing block of the main shaft system can improve the design freedom and reduce the material cost.

[0100] The second bearing housing in the main shaft system is integrally designed with the external gear ring of the gearbox, which can eliminate the assembly process, reduce the number of bolts used, thereby reducing costs. In addition, it can also reduce the cumulative assembly error.

[0101] In the main shaft system, the sliding bearing and the rolling bearing are arranged face to face or back to back, which reduces the axial end play and improves the stability of the torque at the output end.

[0102] The sliding bearing can achieve axial, radial and angular adjustment of the bearing bush assembly.

[0103] The sliding bearing can reduce the wear caused by eccentricity, improve the problem of unstable low-speed start, and improve the stability of the output torque.

[0104] Although the exemplary embodiments of the present invention have been specifically described with reference to its exemplary embodiments, those skilled in the art should understand that various changes in form and details can be made without departing from the spirit and scope of the present invention defined by the claims.

Claims

1. A main shaft system of a wind turbine generator, characterized in that The main shaft system includes: A first bearing housing (11) and a second bearing housing (12) separated from each other. The first bearing housing (11) has a first mounting hole (11a), and the second bearing housing (12) has a second mounting hole (12a). The first mounting hole (11a) and the second mounting hole (12a) are coaxially arranged. A main shaft (40) installed in the first mounting hole (11a) and the second mounting hole (12a). The first end (41) of the main shaft (40) is close to the first bearing housing (11) and is used to connect with the impeller of the wind turbine generator, and the second end (42) of the main shaft (40) is close to the second bearing housing (12) and is used to connect with the gearbox of the wind turbine generator. A first bearing assembly and a second bearing assembly. The first bearing assembly is arranged between the first bearing housing (11) and the main shaft (40), and the second bearing assembly is arranged between the second bearing housing (12) and the main shaft (40). Wherein, the first bearing assembly includes a sliding bearing (100), and the second bearing assembly includes a rolling bearing.

2. The main shaft system of the wind turbine according to claim 1, characterized in that, The second bearing housing (12) is integrally formed with the outer gear ring (30) of the gearbox.

3. The main shaft system of the wind turbine according to claim 1, characterized in that, The first bearing assembly includes a plurality of sliding bearings (100) distributed circumferentially along the main shaft (40).

4. The main shaft system of the wind turbine according to claim 3, characterized in that, Each of the sliding bearings (100) includes a support substrate (110), a bearing bush assembly (120), and an adjustment assembly connecting the support substrate (110) and the bearing bush assembly (120). The adjustment assembly can make the bearing bush assembly (120) move axially and radially relative to the support substrate (110) and can adjust the inclination angle of the bearing bush assembly (120) relative to the support substrate (110).

5. The main shaft system of the wind turbine according to claim 1, characterized in that, The rolling bearing is a tapered roller bearing (200), and the tapered roller bearing (200) includes an outer ring (210), an inner ring (220), and tapered rollers (230) arranged between the outer ring (210) and the inner ring (220).

6. The main shaft system of the wind turbine according to claim 5, characterized in that From the first end (41) to the second end (42) of the main shaft (40), the inclination direction of the rotation axis (R) of the tapered rollers (230) relative to the axis (L) of the main shaft (40) is opposite to the inclination direction of the bearing bush surface (120a) of the sliding bearing (100) relative to the axis (L) of the main shaft (40).

7. The main shaft system of the wind turbine according to claim 6, characterized in that, From the first end (41) to the second end (42) of the main shaft (40), the bearing bush surface (120a) of the sliding bearing (100) is inclined in a direction away from the axis (L) of the main shaft (40), and the rotation axis (R) of the tapered rollers (230) is inclined in a direction close to the axis (L) of the main shaft (40).

8. The main shaft system of a wind turbine according to claim 6, characterized in that, From the first end (41) to the second end (42) of the main shaft (40), the bearing surface (120a) of the sliding bearing (100) is inclined in a direction approaching the axis (L) of the main shaft (40), and the axis of rotation (R) of the tapered roller (230) is inclined in a direction away from the axis (L) of the main shaft (40).

9. The main shaft system of the wind turbine according to claim 3, characterized in that, The number of the sliding bearings (100) located below the center line of the main shaft (40) is greater than the number of the sliding bearings (100) located above the center line of the main shaft (40).

10. A wind turbine generator, characterized in that, The wind power generating set includes a main shaft system according to any one of claims 1 to 9.

Images