WO2023123506A1 - Bearing assembly for wind turbine - Google Patents

Abstract

A bearing assembly for a wind turbine, comprising: a rotating shaft (1) connected to a generator rotor, a bearing seat (2) connected to a generator base, and a front bearing component (31) and a rear bearing component (32) that are disposed between the rotating shaft (1) and the bearing seat (2). Both the front bearing component (31) and the rear bearing component (32) are sliding bearings (3); each sliding bearing (3) comprises a bearing body (36) and multiple radial pads (33), the multiple radial pads (33) being fixedly mounted on the inner side of the bearing body (36) and being arranged at intervals in the circumferential direction of the rotating shaft (1); the inner side surface of each radial pad (33) is a radial bearing surface bearing a radial load of the rotating shaft (1), and the radial bearing surface is provided with a first wear-resistant insulating layer (331). Thus, a shaft current insulation effect is improved, and the operation and maintenance are convenient.

Description

Bearing assembly for wind power generator technical field

The invention relates to the field of wind power generation, in particular to a bearing assembly for a wind power generator.

Background technique

In recent years, with the rapid development of offshore wind power generation technology, semi-direct drive generators have become one of the mainstream models of offshore wind power, and rolling bearing units are important supporting components of semi-direct drive generators. During the operation of the wind turbine, due to balance, air gap, load, friction, wiring and other reasons, it is easy to generate a potential difference near the rolling bearing unit, and it is easy to cause electric corrosion to the rolling bearing raceway and rolling body in the rolling bearing unit, which will cause damage to the rolling bearing, resulting in Problems such as abnormal noise and excessive vibration affect the service life of rolling bearings; and the rolling bearings used in wind turbines are large-sized bearings, which are difficult and costly to replace when damaged. Especially with the increasing power requirements of semi-direct drive generator sets, the problem of electric corrosion and damage to rolling bearings caused by shaft currents will become more serious. However, the large-sized rolling bearings for wind power generators are not only inconvenient to install shaft current insulating parts, but also the manufacturing of the insulating parts is difficult and the installation cost is high.

Contents of the invention

The technical problem to be solved by the present invention is to overcome the deficiencies of the prior art and provide a bearing assembly for wind power generators with good shaft current insulation effect and convenient operation and maintenance.

In order to solve the problems of the technologies described above, the technical solution proposed by the present invention is:

A bearing assembly for a wind power generator, comprising a rotating shaft connected to the generator rotor, a bearing seat connected to the generator base, and a front bearing part and a rear bearing part arranged between the rotating shaft and the bearing seat, the Both the front bearing component and the rear bearing component are sliding bearings, and the sliding bearing includes a bearing body and a plurality of radial pads, and a plurality of radial pads are arranged at intervals along the inner circumferential direction of the rotating shaft; the radial pads The inner surface of the inner surface is a radial bearing surface for bearing the radial load of the rotating shaft, and the radial bearing surface is provided with a first wear-resistant insulating layer.

As a further improvement of the above technical solution:

The front bearing part and/or the rear bearing part are provided with multiple sets of thrust pad units, the number of the thrust pad units is the same as the number of the radial pads, and the thrust pad units are arranged adjacent Between the radial pads; each set of thrust pad units includes a thrust pad set on the inner end surface of the bearing body, and the outer end surface of the thrust pad is an axial bearing surface that bears the axial load of the rotating shaft. The axial bearing surface is provided with a second wear-resistant insulating layer.

The inner surface of the bearing body is provided with a thrust pad mounting block, and the radial pad is limitedly installed between adjacent thrust pad mounting blocks, and the radial bearing surface of the radial pad is higher than the thrust The inner surface of the shoe installation block; the thrust shoe is installed on one side of the thrust shoe installation block, and the axial bearing surface of the thrust shoe is higher than the end surface of the bearing body.

An axial insulating pad is provided between the thrust pad and the thrust pad mounting block, and a radial insulating pad is provided between the radial pad and the bearing body.

Both the first wear-resistant insulating layer and the second wear-resistant insulating layer are polytetrafluoroethylene layers or polyether ether ketone layers.

The bearing assembly for wind power generators also includes oil supply passages arranged on the front bearing part and the rear bearing part, the oil supply passages include radial pad oil injection holes and thrust pad oil injection holes, and the radial pad oil injection holes The spray end of the hole is set between adjacent radial pads or on the radial pad; the thrust pad oil injection hole is set on the thrust pad.

The sliding bearing also includes a housing of the bearing body, a swing adjustment part that ensures the self-adaptive swing of the bearing body along with the rotating shaft, and a first stopper that limits the swing range of the bearing body, wherein the bearing body can be adjusted through the swing adjustment part. It is swingably installed in the housing of the bearing body, and the first limiting member is arranged at the position of the swing regulating part.

The sliding bearing also includes an self-aligning block that ensures the self-adaptive swing of the radial shoe along with the rotating shaft, and a second limiter that limits the swing range of the radial shoe, wherein the self-aligning block is installed on the radial shoe , and located between the radial pad and the bearing body; the outer side of the self-aligning block is provided with an adjustment spherical surface that is oscillatingly matched with the bearing body; the second limiter is arranged on the self-aligning block and the bearing body.

The rear side of the rear bearing part is provided with a rear bearing oil retaining chamber that provides lubricating oil for the first wear-resistant insulating layer when the oil is cut off, and a sealing assembly that prevents lubricating oil from leaking from the rear side of the rear bearing part to the motor. The rear bearing oil retention cavity is arranged between the rear bearing component and the sealing assembly.

The sealing assembly includes an oil deflecting ring, an inner sealing ring and an outer sealing ring, wherein the oil deflecting ring is sleeved on the rotating shaft and can rotate with the rotating shaft; the inner sealing ring and the The outer sealing ring is sleeved outside the oil deflecting ring in turn, a first sealing passage is left between the inner sealing ring and the oil deflecting ring, and a second sealing channel is left between the outer sealing ring and the oil deflecting ring. Two sealing passages; along the radial direction of the rotating shaft, the first sealing passage is located inside the second sealing passage to form an oil retaining step.

The inner side of the oil deflecting ring is provided with a rear bearing oil seal ring, and the rear bearing oil retaining cavity is formed by surrounding the rear bearing oil seal ring, the rear bearing component and the rotating shaft; the rear bearing A third sealing passage is provided between the oil sealing ring and the rotating shaft.

The inner side of the oil deflecting ring is provided with an annular oil deflecting edge, and the annular oil deflecting edge and the rear bearing oil sealing ring are enclosed to form a splash-proof area to prevent the lubricating oil from splashing when the rotating shaft rotates. The annular oil deflecting edge There is an oil gap between the edge and the rear bearing oil seal ring; the inner upper half of the inner seal ring is provided with an arc-shaped oil retaining edge, and along the radial direction of the rotating shaft, the arc-shaped oil retainer The edge is located on the outer side of the annular oil deflector.

The first sealing passage, the second sealing passage and/or the third sealing passage are provided with sealing protrusions which block the passage of part of lubricating oil; the height of the sealing protrusions is smaller than that of the corresponding sealing passages.

The lower half of the bearing seat is provided with an oil discharge channel, and the oil inlet end of the oil discharge channel communicates with the flow space between the inner seal ring and the rear bearing oil seal ring, and the inner seal ring and the flow space between the outer sealing ring.

The lower half of the front side of the front bearing component is enclosed by the front bearing oil retaining ring to form a front bearing oil retaining cavity, the front bearing oil retaining ring is sleeved on the rotating shaft, and the front bearing oil retaining cavity The inner surface of the ring is provided with a sealing protrusion, and there is an overflow gap between the sealing protrusion and the rotating shaft.

The sliding bearing also includes multiple sets of limit adjustment units, the radial pad located in the lower half of the bearing body is in contact with the bearing body, and the radial pad located in the upper half of the bearing body is in contact with the bearing body. There is an adjustment gap to prevent the lock-up of the rotation shaft; the adjustment gap is kept unchanged by the limit adjustment unit arranged between the radial pad and the bearing body when the rotation shaft is working normally, and the adjustment gap is kept unchanged during the rotation The shaft expands to contract when in contact with the radial pads.

The limit adjustment unit includes an elastic adjustment member and a pad limiter, the elastic adjuster is compressed and arranged at the position of the adjustment gap; the pad limiter is connected between the radial pad and the Between the bearing bodies, and between the pad stopper and the radial pads or the bearing body, there is an escape groove for the radial pads to expand outward.

The elastic adjusting member is a cylindrical spring; the bearing body and the radial pad are provided with spring installation grooves correspondingly to form a spring placement area; the cylindrical spring is compressed and arranged in the spring placement area.

The elastic adjusting member is a butterfly spring, and the butterfly spring is limitedly installed at the adjustment gap by a positioning pin; the bearing body and the radial pad are correspondingly provided with positioning pin installation grooves to form a positioning pin. pin placement area.

The pad limiter is a limit screw, and the avoidance groove is set on the bearing body or the radial pad; when the avoidance groove is set on the bearing body, the tail of the limit screw end is threaded with the radial tile; when the avoidance groove is set on the radial tile, the tail end of the limit screw is threaded with the bearing body; the head end of the limit screw is elastically Under the action of the adjusting part, it is limitedly matched with the avoidance groove.

Compared with the prior art, the present invention has the advantages of:

In the present invention, the front bearing part and the rear bearing part of the wind power generator are set as sliding bearings, so as to change the traditional wind power generator from rolling bearing bearing to sliding bearing bearing. Low weight and small volume requirements at high power. At the same time, the sliding bearing is provided with a bearing body and multiple radial pads in the form of splits. The radial pads are fixedly installed inside the bearing body and arranged at intervals along the circumference of the rotating shaft. The radial pads in the form of splits can reliably bear the rotating shaft It can be easily processed while radial load is applied. The radial bearing surface of the radial tile is provided with a first wear-resistant insulating layer to effectively isolate the shaft current and avoid the occurrence of electric corrosion of the bearing, and the radial tile is set in a separate form to facilitate the forming and effective arrangement of the wear-resistant insulating layer , Its operability is strong, processing and maintenance are convenient.

Description of drawings

Hereinafter, the present invention will be described in more detail based on the embodiments with reference to the accompanying drawings. in:

Fig. 1 is a sectional view of a bearing assembly for a wind power generator according to the present invention.

Fig. 2 is an enlarged view of the upper half of the bearing assembly for the wind power generator of the present invention.

Fig. 3 is an enlarged view of part A of Fig. 2 of the present invention.

Fig. 4 is an enlarged view of the lower half of the bearing assembly for the wind power generator of the present invention.

Fig. 5 is a three-dimensional structural schematic view of the rear bearing component in Embodiment 1 of the present invention.

Fig. 6 is another three-dimensional structural schematic view of the rear bearing component in Embodiment 1 of the present invention.

Fig. 7 is a schematic perspective view of the three-dimensional structure of the bearing shell of the present invention.

FIG. 8 is a schematic perspective view of the three-dimensional structure of the bearing body in FIG. 6 .

Fig. 9 is a schematic diagram of the three-dimensional structure of the radial tile of the present invention.

Fig. 10 is a schematic diagram of the three-dimensional structure of the thrust pad of the present invention.

Fig. 11 is a schematic perspective view of the three-dimensional structure of the radial insulating pad of the present invention.

Fig. 12 is a schematic perspective view of the three-dimensional structure of the axial insulation pad of the present invention.

Fig. 13 is a perspective view of the structure of the front bearing part of the present invention.

Fig. 14 is a sectional view of the rear bearing oil seal ring of the present invention.

Fig. 15 is a cross-sectional view of the oil slinger of the present invention.

Fig. 16 is a sectional view of the inner sealing ring of the present invention.

Fig. 17 is a cross-sectional view of the outer sealing ring of the present invention.

Fig. 18 is a schematic perspective view of the three-dimensional structure of the oil slinger of the front bearing of the present invention.

Fig. 19 is a front sectional view of the rear bearing member of the present invention.

Fig. 20 is a schematic perspective view of the rear bearing in Embodiment 2 of the present invention.

Fig. 21 is a front view of the rear bearing of Embodiment 2 of the present invention.

Fig. 22 is a sectional view of the B-B section in Fig. 21 .

Fig. 23 is an enlarged view of part C in Fig. 22 .

Fig. 24 is another front view of the rear bearing of Embodiment 2 of the present invention.

Fig. 25 is a sectional view of the D-D section of Fig. 24 (the elastic element is a cylindrical spring).

Fig. 26 is a cross-sectional view taken along line E-E of Fig. 25 .

Fig. 27 is a sectional view of the D-D section of Fig. 24 (the elastic element is a Belleville spring).

Fig. 28 is a cross-sectional view taken along the line F-F of Fig. 27 .

Fig. 29 is a schematic perspective view of the front bearing component in Embodiment 2 of the present invention.

Each label in the figure means:

1. Rotating shaft; 2. Bearing seat; 3. Sliding bearing; 31. Front bearing component; 311. Front retaining ring; 32. Rear bearing component; 33. Radial tile; 331. First wear-resistant insulating layer; 332. Radial insulation pad; 34, thrust tile unit; 341, thrust tile; 342, second wear-resistant insulating layer; 343, axial insulation pad; 35, bearing body shell; 36, bearing body; 37, thrust tile installation block; 38. Swing adjustment part; 381. Spherical protrusion; 382. Spherical groove; 39. Self-aligning block; 391. Regulating spherical surface; 4. Sealing protrusion; 5. Oil supply part; 51. Oil supply channel; 511. Diameter 512, annular oil supply groove; 513, radial tile oil injection hole; 514, thrust tile oil injection hole; 515, annular oil inlet groove; 52, oil inlet channel; 521, horizontal oil inlet section; 522, vertical Straight into the oil section; 6. Rear bearing oil retention cavity; 61. Rear bearing oil seal ring; 7. Seal assembly; 71. Oil retaining ring; 711. Ring oil retaining edge; 712. Splash prevention area; Gap; 72, inner sealing ring; 721, arc-shaped oil retaining edge; 73, outer sealing ring; 74, flow space; 75, first sealing channel; 76, second sealing channel; 77, third sealing channel; 8 , oil discharge channel; 81, oil inlet end; 9, front bearing oil retaining cavity; 91, front bearing oil retaining ring; 92, overcurrent gap; 10, limit adjustment unit; 101, elastic adjustment piece; Shape spring; 1012, butterfly spring; 102, tile limit piece; 1021, limit screw; 103, avoidance groove; 104, spring placement area; 105, positioning pin; 106, positioning pin placement area; 107, adjustment gap .

Detailed ways

The present invention will be described in further detail below in conjunction with the accompanying drawings and specific embodiments, but the protection scope of the present invention is not limited thereby.

Example 1

As shown in FIGS. 1 to 18 , the bearing assembly for a wind power generator in this embodiment includes a rotating shaft 1 , a bearing housing 2 , a front bearing component 31 and a rear bearing component 32 . Among them, the rotating shaft 1 is connected with the rotor of the generator, and is used to transmit the torque and load of the rotor of the wind turbine, and is a rotating part; the bearing seat 2 is connected with the base of the generator, and bears the weight and other loads of the rotor of the wind turbine, and is a stationary component. Components; the front bearing part 31 and the rear bearing part 32 are arranged between the rotating shaft 1 and the bearing seat 2 to support the normal operation of the rotating shaft 1 and the parts between the rotating shaft 1 during the rotation. In this embodiment, both the front bearing component 31 and the rear bearing component 32 are sliding bearings 3 , and the sliding bearing 3 includes a bearing body 36 and a plurality of radial pads 33 . Wherein, a plurality of radial pads 33 are fixedly mounted on the inner side of the bearing body 36, and the plurality of radial pads 33 are arranged at intervals along the circumference of the rotating shaft 1, and the radial pads 33 can bear the radial load of the rotating shaft 1 to ensure rotation Rotational accuracy of axis 1. The inner surface of the radial shoe 33 is a radial bearing surface for bearing the radial load of the rotating shaft 1 , and the radial bearing surface is provided with a first wear-resistant insulating layer 331 .

In the present invention, the front bearing part 31 and the rear bearing part 32 for the wind power generator are set as the sliding bearing 3, so as to change the traditional wind power generator using rolling bearing bearings into the bearing bearing of the sliding bearing 3, which has a compact structure and takes up little space, meeting the requirements The demand for low weight and small volume of wind turbines at high power. At the same time, the sliding bearing 3 is provided with a bearing body 36 and radial pads 33 in split form. The radial pads 33 are fixedly installed inside the bearing body 36 and arranged at intervals along the circumference of the rotating shaft 1. The radial pads 33 in split form While reliably bearing the radial load of the rotating shaft 1, it can be processed conveniently. The radial bearing surface of the radial tile 33 is provided with a first wear-resistant insulating layer 331 to effectively isolate the shaft current and avoid the occurrence of bearing electric corrosion, and the radial tile 33 is separately arranged to facilitate the first wear-resistant insulating layer The molding and effective layout of 331 have strong operability and convenient processing and maintenance.

As shown in FIGS. 5 and 6 , the rear bearing part 32 is provided with multiple sets of thrust shoe units 34 . The number of thrust shoe units 34 is the same as the number of radial shoes 33 , and the thrust shoe units 34 are arranged between adjacent radial shoes 33 . The thrust shoe unit 34 includes a thrust shoe 341 disposed on the inner end surface of the bearing body 36 to bear the axial load of the rotating shaft 1 and avoid the axial movement of the rotating shaft 1 . The combination of the thrust pad 341 and the radial pad 33 effectively bears the axial and radial loads of the rotating shaft 1, and at the same time realizes a reasonable and compact layout of the load components.

As shown in Figure 10, the outer end surface of the thrust pad 341 is an axial bearing surface for bearing the axial load of the rotating shaft 1; the axial bearing surface is provided with a second wear-resistant insulating layer 342 to effectively isolate the shaft current and avoid bearing electric corrosion phenomenon; at the same time, the separate arrangement of the thrust tile 341 facilitates the formation and effective arrangement of the second wear-resistant insulating layer 342, which has strong operability and convenient processing and maintenance. In other embodiments, as shown in FIG. 13 , the thrust pad 341 can also be arranged on the front bearing component 31 to ensure that at least one of the bearing components bears the axial load of the rotating shaft 1 .

Due to the many and complicated working conditions of the wind power generator, the present invention needs to comprehensively consider factors such as the load size and time of each working condition to adjust the distribution of the radial pads 33, so as to improve the bearing capacity and service life of the bearing. As shown in FIG. 5 , the radial pads 33 can be arranged evenly along the circumference of the rotating shaft 1 ; meanwhile, as shown in FIG. 6 , under complex working conditions, the radial pads 33 can also be arranged non-uniformly along the circumference of the rotating shaft 1 .

In this embodiment, each set of thrust shoe units 34 has one thrust shoe 341 , and the thrust shoe 341 is arranged on the end surface of the inner side of the bearing body 36 close to the axial bearing position. In other embodiments, when it is necessary to bear the axial reaction force of the rotating shaft 1 , there may be two thrust pads 341 , and the two thrust pads 341 are arranged on both ends of the inner side of the bearing body 36 .

As shown in FIG. 5 , FIG. 6 and FIG. 8 , a thrust pad mounting block 37 is provided on the inner surface of the bearing body 36 . The radial shoe 33 is limitedly installed between adjacent thrust shoe mounting blocks 37 , and the radial bearing surface of the radial shoe 33 is higher than the inner surface of the thrust shoe mounting block 37 to effectively bear the radial load of the rotating shaft 1 . The thrust pad 341 is installed on one side of the thrust pad mounting block 37 , and the axial bearing surface of the thrust pad 341 is higher than the end surface of the bearing body 36 to effectively bear the axial load of the rotating shaft 1 .

At the same time, the thrust pad mounting block 37 and the bearing body 36 are integrally formed. In other embodiments, the thrust pad mounting block 37 can also be assembled and connected with the bearing body 36 . As shown in FIG. 9 and FIG. 10 , the radial pad 33 is an arc-shaped radial pad, and the thrust pad 341 is a block thrust pad.

As shown in FIG. 12 , an axial insulating pad 343 is provided between the thrust pad 341 and the thrust pad mounting block 37 . As shown in FIG. 11 , a radial insulating pad 332 is provided between the radial shoe 33 and the bearing body 36 . In order to achieve double insulation and further isolate the shaft current. As shown in FIG. 3 , the bearing body 36 , the radial insulating pad 332 and the radial shoe 33 are connected as a whole by fasteners.

In this embodiment, both the first wear-resistant insulating layer 331 and the second wear-resistant insulating layer 342 are polytetrafluoroethylene layers or polyetheretherketone layers. Since the rotating shaft 1 is cast iron with low hardness, the polytetrafluoroethylene layer or polyetheretherketone layer of soft material can effectively avoid the wear of the rotating shaft 1 during rotation and improve the service life of the rotating shaft 1; at the same time, polytetrafluoroethylene The vinyl fluoride layer or polyether ether ketone layer has self-lubricating properties, and its friction coefficient is low, which can be effectively applied to oil-cut dry grinding conditions and marginal friction states.

As shown in FIG. 1 and FIG. 2 , the bearing assembly for a wind power generator further includes an oil supply component 5 . The oil supply part 5 includes an oil inlet passage 52 and an oil supply passage 51 which communicate with each other. The oil inlet passage 52 is arranged on the bearing housing 2 ; the oil supply passage 51 is arranged on the front bearing part 31 and the rear bearing part 32 . As shown in Figure 6 and Figure 13, the oil supply channel 51 includes a radial pad oil injection hole 513 and a thrust pad oil injection hole 514, and the discharge end of the radial pad oil injection hole 513 is arranged between adjacent radial pads 33 The thrust shoe mounting block 37 or the radial shoe 33 to provide lubricating oil to the first wear-resistant insulating layer 331; the thrust shoe oil injection hole 514 is arranged on the thrust shoe 341 to provide lubrication to the second wear-resistant insulating layer 342 Oil.

Further, the oil inlet channel 52 includes a horizontal oil inlet section 521 and two vertical oil inlet sections 522 . Wherein, the horizontal oil inlet section 521 is connected with an external oil inlet source; one end of the two vertical oil inlet sections 522 is connected with the horizontal oil inlet section 521, and the other ends of the two vertical oil inlet sections 522 are connected with the front bearing part 31 and the rear bearing respectively. The oil supply passage 51 of the component 32 communicates. The present invention can simultaneously realize the effective oil supply of the front bearing part 31 and the rear bearing part 32 through one oil supply source.

As shown in FIGS. 5 to 8 , the sliding bearing 3 further includes a bearing shell 35 , a swing adjustment portion 38 and a first limiting member. Wherein, the swing adjustment part 38 is arranged between the bearing body 36 and the bearing body housing 35, and the bearing body 36 is swingably installed in the bearing body housing 35 through the swing adjustment part 38, so as to ensure that the bearing body 36 swings adaptively with the rotating shaft 1 , so that the radial bearing surface of the radial tile 33 can be adaptively adjusted, which greatly improves the bearing capacity, reduces the vibration of the rotating shaft system, effectively solves the problem of the large bearing capacity of the rotating shaft 1, and improves the wind turbine rotating shaft system. stability and service life. At the same time, the first limiter is arranged at the position of the swing adjustment part 38, and the first limiter is connected between the bearing body 36 and the bearing body shell 35, so as to limit the bearing body 36 while providing the space for the radial shoe 33 to swing. swing range.

The rotating shaft 1 of the present invention will be tilted in the bearing assembly for wind power generators, and uneven loads will easily occur. Through the setting of the swing adjustment part 38, the radial pad 33 and the bearing body 36 can be adjusted when the rotating shaft 1 deflects. It deflects with the rotating shaft 1 to ensure load balance, and effectively avoids problems such as eccentric wear, vibration and tile burning caused by load deflection.

Further, as shown in FIG. 3 , the oil supply channel 51 also includes a radial oil delivery hole 511 and an annular oil supply groove 512 connected in sequence. Wherein, the radial oil delivery hole 511 and the annular oil supply groove 512 are both arranged on the bearing shell 35 , and the radial shoe oil injection hole 513 and the thrust shoe oil injection hole 514 are both connected to the annular oil supply groove 512 . The present invention realizes the function that one oil supply source can supply oil to each wear-resistant insulation layer at the same time through the arrangement of the annular oil supply groove 512, and the structure is simple and the oil supply effect is good.

As shown in Figures 7 and 8, the swing adjustment part 38 includes a spherical protrusion 381 and a spherical groove 382 that cooperate with each other. The spherical protrusion 381 is arranged on the bearing body 36, and the spherical groove 382 is arranged on the bearing body shell 35 to accommodate load changes. Simultaneously, the first spacer includes a spacer pin and a spacer hole, the spacer hole is located between the bearing body 36 and the bearing housing 35, the spacer pin is penetrated in the spacer hole, and the spacer pin and the spacer A swing gap is left between the holes to limit the swing range of the bearing body 36 while providing the swing space for the radial pad 33 .

Meanwhile, the bearing shell 35 is two semi-annular shells, and the two half-annular shells are detachably connected by fasteners. The radial pad 33 is installed on the inner surface of the bearing body 36 by screws, which makes the installation and disassembly of the bearing assembly convenient and convenient for later maintenance.

As shown in FIGS. 1 to 4 , a rear bearing oil retention cavity 6 and a sealing assembly 7 are provided on the rear side of the rear bearing component 32 . Wherein, the rear bearing oil retaining chamber 6 is arranged between the rear bearing component 32 and the sealing assembly 7, so that it can continue to supply lubricating oil to the first wear-resistant insulating layer 331 when the oil supply component 5 cuts off the oil. The sealing assembly 7 can effectively block the lubricating oil, so that the lubricating oil is discharged from the front side of the front bearing part 31 to the external oil chamber, preventing the lubricating oil from being discharged from the rear side of the rear bearing part 32 and affecting the motor parts.

Further, the seal assembly 7 includes an oil deflector ring 71 , an inner seal ring 72 and an outer seal ring 73 . Wherein, the oil deflecting ring 71 is sleeved on the rotating shaft 1, and the oil deflecting ring 71 is in interference fit with the rotating shaft 1, and the oil deflecting ring 71 can rotate with the rotating shaft 1; the inner sealing ring 72 and the outer sealing ring 73 are sleeved sequentially Outside the oil deflecting ring 71 , a first sealing passage 75 is left between the inner sealing ring 72 and the oil deflecting ring 71 , and a second sealing passage 76 is left between the outer sealing ring 73 and the oil deflecting ring 71 . The arrangement of the first sealing channel 75 and the second sealing channel 76 forms a multi-stage blocking channel, which plays a role of blocking lubricating oil layer by layer, preventing the lubricating oil from being discharged from the rear side of the rear bearing component 32 . At the same time, the sealing structure of the present invention is arranged compactly in the limited space between the rotating shaft 1 and the bearing seat 2, and achieves excellent anti-leakage function.

At the same time, along the radial direction of the rotating shaft 1, the first sealing passage 75 is located inside the second sealing passage 76 to form an oil retaining step to prevent the sealing oil leaked from the first sealing passage 75 from being directly discharged from the second sealing passage 76, Guaranteed the oil blocking effect.

In this embodiment, a rear bearing oil sealing ring 61 is provided inside the oil deflecting ring 71 . The rear bearing oil retaining cavity 6 is enclosed and formed by the rear bearing oil seal ring 61 , the rear bearing component 32 and the rotating shaft 1 . Further, a third sealing channel 77 is provided between the rear bearing oil sealing ring 61 and the rotating shaft 1 , which further prevents lubricating oil from being discharged from the rear side of the rear bearing component 32 . In this embodiment, both the inner sealing ring 72 and the outer sealing ring 73 are fixedly installed on the bearing housing 2 through fasteners. The rear bearing oil sealing ring 61 is fixedly installed on the bearing shell 35 through fasteners.

As shown in Figure 3 and Figure 15, the inner side of the oil deflector ring 71 is provided with an annular oil deflector 711, and the annular oil deflector 711 is surrounded by the rear bearing oil seal ring 61 to form an anti-splash area 712, so that the lubricating oil splashes and forms The oil mist-like oil body flows down along the annular oil baffle 711 to prevent the lubricating oil from splashing when the rotating shaft 1 rotates. There is an oil gap 713 between the annular oil deflecting edge 711 and the rear bearing oil sealing ring 61 for passing lubricating oil and facilitating the rotation of the oil deflecting ring 71 . At the same time, as shown in FIG. 16 , the inner upper half of the inner sealing ring 72 is provided with an arc-shaped oil retaining edge 721 . Along the radial direction of the rotating shaft 1 , the arc-shaped oil deflecting edge 721 is located outside the annular oil deflecting edge 711 to further effectively prevent splashing of lubricating oil.

As shown in FIG. 2 and FIG. 3 , the first sealing channel 75 , the second sealing channel 76 and the third sealing channel 77 are provided with sealing protrusions 4 ; the height of the sealing protrusions 4 is smaller than that of the corresponding sealing channels. In order to block part of the lubricating oil from passing through, it can avoid the high temperature and heat generation of the bearing caused by completely blocking the lubricating oil, and it will not hinder the effective rotation of the oil deflector ring 71 . In other embodiments, the sealing protrusion 4 may also be provided on only one of the first sealing channel 75 , the second sealing channel 76 and the third sealing channel 77 .

In this embodiment, the sealing protrusion 4 is a rigid sealing member. The sealing protrusion 4 of the first sealing passage 75 is arranged on the inner sealing ring 72, the sealing protrusion 4 of the second sealing passage 76 is arranged on the outer sealing ring 73, and the sealing protrusion 4 of the third sealing passage 77 is arranged on the rear bearing On the oil seal ring 61.

As shown in FIG. 4 , the lower half of the bearing seat 2 is provided with an oil discharge channel 8 . The oil inlet end 81 of the oil discharge channel 8 communicates with the flow space 74 between the inner seal ring 72 and the rear bearing oil seal ring 61, and the flow space 74 between the inner seal ring 72 and the outer seal ring 73, so that the rear The blocked lubricating oil at the rear side of the bearing part 32 is effectively discharged.

As shown in Fig. 2, Fig. 4 and Fig. 18, the lower half of the front side of the front bearing component 31 is enclosed by the front bearing oil retaining ring 91 to form a front bearing oil retention cavity 9, so as to protect the lower half of the front bearing component 31. Oil retention is carried out at the part, so that the first wear-resistant insulating layer 331 at the lower part of the front bearing part 31 can continue to provide lubricating oil when the oil supply part 5 cuts off the oil.

In this embodiment, the front bearing oil deflecting ring 91 is sleeved on the rotating shaft 1, and the inner surface of the front bearing oil deflecting ring 91 is provided with a sealing protrusion 4, and there is an overflow gap between the sealing protrusion 4 and the rotating shaft 1 92, so as to block the passage of part of the lubricating oil while avoiding the occurrence of the high temperature heating problem of the bearing caused by completely blocking the passage of the lubricating oil. Simultaneously, the front bearing component 31 is compressed and limited by the front retaining ring 311 .

Preferably, as shown in FIG. 19 , FIG. 26 and FIG. 28 , the sliding bearing 3 further includes multiple sets of limit adjustment units 10 . The radial pad 33 located in the lower half of the bearing body 36 is in contact with the bearing body 36, and there is an adjustment gap 107 between the radial pad 33 located in the upper half of the bearing body 36 and the bearing body 36; the adjustment gap 107 is normal on the rotating shaft 1 During operation, the limit adjustment unit 10 remains unchanged, and the adjustment gap 107 shrinks when the rotating shaft 1 expands to contact with the radial shoe 33 . The limit adjustment unit 10 is arranged between the radial shoe 33 and the bearing body 36 to control and adjust the radial position of the radial shoe 33 .

Simultaneously, since the lower half of the bearing body 36 is the load-bearing area of the rotating shaft 1, the present invention contacts the radial pad 33 positioned at the lower half of the bearing body 36 with the bearing body 36, which can effectively bear the load of the rotating shaft 1, ensuring that the bearing components carrying capacity. The upper half of the bearing body 36 is the non-load bearing area of the rotating shaft 1. In the present invention, an adjustment gap 107 is left between the radial pad 33 and the bearing body 36 on the upper half of the bearing body 36. The adjustment gap 107 is normal on the rotating shaft 1. When working, the limit adjustment unit 10 remains unchanged, and the adjustment gap 107 shrinks when the rotating shaft 1 expands to contact with the radial shoe 33, which makes the rotating shaft 1 have a certain expansion space when heated and expands, effectively avoiding the rotation of the rotating shaft. 1. The locking phenomenon caused by friction, heat and expansion improves the service life of the bearing and ensures the safe and reliable operation of the bearing. It can be seen that the present invention can effectively prevent the locking phenomenon of the rotating shaft 1 while ensuring the bearing capacity of the bearing, so that the bearing components can operate reliably and safely under normal operation and oil cut-off conditions.

In this embodiment, the limit adjustment unit 10 includes an elastic adjustment member 101 and a pad limit member 102 . The elastic adjusting member 101 is compressed and arranged at the position of the adjusting gap 107. The elastic adjusting member 101 can be compressed when the rotating shaft 1 expands. At this time, the radial shoe 33 expands outward to prevent the rotating shaft 1 from locking.

At the same time, the pad limiter 102 is connected between the radial pad 33 and the bearing body 36 to limit the position of the radial pad 33 and prevent the upper half of the radial pad 33 from contacting and rubbing against the rotating shaft 1 . An avoidance groove 103 is provided between the pad limiter 102 and the bearing body 36 , and the arrangement of the avoidance groove 103 provides a space for the radial pad 33 to expand outward when the adjustment gap 107 is narrowed. In other embodiments, the setting position of the avoidance groove 103 only needs to ensure that the radial shoe 33 has an outward expansion space while being reliably limited. For example, the avoidance groove 103 can also be arranged on the radial shoe 33 .

When the rotating shaft 1 is in normal operation, the pad limiter 102 cooperates with the avoidance groove 103 under the action of the elastic adjusting member 101 to fix the position of the radial pad 33. At this time, the radial pad 33 and the rotating shaft 1 A certain gap is maintained to avoid phenomena such as a large degree of freedom of rotation of the rotating shaft 1 caused by an excessive gap between the radial pad 33 and the rotating shaft 1, so as to ensure the safe operation of the rotating shaft 1 during normal operation. When the oil is cut off, the rotating shaft 1 expands due to heat generated by friction. When the rotating shaft 1 expands to contact the radial pad 33 located on the upper half of the bearing body 36, the radial pad 33 expands and the adjustment gap 107 shrinks. , the pad stopper 102 moves in the avoidance groove 103 to provide space for the radial pad 33 to expand outward.

In this embodiment, the elastic adjusting member 101 is a cylindrical spring 1011 . The bearing body 36 and the radial pad 33 are correspondingly provided with spring installation grooves to form the spring placement area 104; the cylindrical spring 1011 is arranged in the spring placement area 104 in a compressed state. It makes the radial pad 33 in a fixed state when the rotating shaft 1 is working normally, and can expand stably when the rotating shaft 1 expands, ensuring that the bearing components can operate reliably and safely under normal working conditions and oil cut-off conditions, and has a simple structure Compact and takes up little space.

Further, the pad limiter 102 is a limit screw 1021; the avoidance groove 103 is arranged on the outer peripheral area of the bearing body 36, and the bearing body 36 is provided with an installation through hole for the limit screw 1021 to pass through, and the avoidance groove 103 is connected to the installation through hole. The holes are connected. The tail end of the limit screw 1021 passes through the avoidance groove 103 and the installation through hole in turn and is threadedly connected with the radial tile 33; The position of the radial shoe 33 is effectively fixed when the rotating shaft 1 works normally.

In other embodiments, the avoidance groove 103 can also be set on the radial pad 33. At this time, the tail end of the limit screw 1021 is threadedly connected with the bearing body 36, and the head end of the limit screw 1021 acts on the elastic adjustment member 101. Cooperate with the escaping groove 103 in a limited position.

Furthermore, each set of limit adjustment units 10 has two limit screws 1021 , and the two limit screws 1021 are respectively arranged on both sides of the elastic adjustment member 101 to further ensure effective fixation and stable outward expansion of the radial tile 33 . In this embodiment, the limit screw 1021 is an insulating screw to further isolate the shaft current.

Further, the relationship between the adjustment gap 107L and the diameter d of the rotating shaft 1 is 0.005d≤L≤0.01d. This enables the setting of the adjustment gap 107 to meet the expansion requirement of the rotating shaft 1 when it is heated and expands, further avoiding the locking phenomenon of the rotating shaft 1 .

Example 2

Fig. 20 to Fig. 29 show another embodiment of the bearing assembly for the wind power generator of the present invention, this embodiment is basically the same as the previous embodiment, the difference is that the sliding bearing 3 of this embodiment cancels the bearing shell 35 and a swing adjustment structure is set between the radial shoe 33 and the bearing body 36. That is, the swing form of setting the self-aligning block 39 between the radial shoe 33 and the bearing body 36 is used instead of the swing form of setting the swing adjustment part 38 between the bearing shell 35 and the bearing body 36, which solves the problem of load deflection. At the same time, the bearing arrangement space is minimized.

Specifically, the sliding bearing 3 further includes an aligning block 39 and a second limiting member. The self-aligning block 39 is installed on the radial pad 33, and the self-aligning block 39 is located between the radial pad 33 and the bearing body 36; It cooperates with the swing of the bearing body 36, which ensures that the radial shoe 33 can self-adaptively swing with the rotating shaft 1; At the same time, the swing range of the bearing body 36 is limited.

The rotating shaft 1 of the present invention will be tilted in the bearing assembly for wind power generators, which is prone to uneven loading. Through the setting of the self-aligning block 39, the radial shoe 33 can follow the rotation shaft 1 when the rotating shaft 1 deflects. Deflection to ensure load balance, effectively avoiding problems such as eccentric wear, vibration and tile burning caused by load deflection.

Preferably, as shown in FIG. 24 , when there is an adjustment gap 107 between the radial pad 33 on the upper half of the bearing body 36 and the bearing body 36 , the self-aligning block 39 is only arranged on the radial pad 39 on the lower half of the bearing body 36 . Go up to tile 33. At this time, the self-aligning block 39 is in contact with the bearing body 36 to ensure the bearing capacity of the rotating shaft 1 while solving the problem of load deflection.

As shown in FIG. 25 and FIG. 26 , the elastic adjusting member 101 is a cylindrical spring 1011 . The bearing body 36 and the radial pad 33 are respectively provided with spring installation grooves to form the spring placement area 104 ; the cylindrical spring 1011 is arranged in the spring placement area 104 in a compressed state. It makes the radial pad 33 in a fixed state when the rotating shaft 1 is working normally, and can expand stably when the rotating shaft 1 expands, ensuring that the bearing components can operate reliably and safely under normal working conditions and oil cut-off conditions, and has a simple structure Compact and takes up little space.

In other embodiments, as shown in FIG. 27 and FIG. 28 , the elastic adjusting member 101 can also be configured as a disc spring 1012. The disc spring 1012 is configured in a compressed state. The disc spring 1012 can be compressed when the rotating shaft 1 expands. This makes the radial shoe 33 in a fixed state when the rotating shaft 1 works normally, and can expand stably to prevent the rotating shaft 1 from locking when the rotating shaft 1 expands.

At the same time, the Belleville spring 1012 is limitedly installed at the adjustment gap 107 through a positioning pin 105 . The bearing body 36 and the radial pad 33 are correspondingly provided with positioning pin installation grooves to form a positioning pin placement area 106 , which has a simple and compact structure and takes up little space. In this embodiment, the positioning pin 105 is an insulating positioning pin to further isolate the shaft current. Further, the radial insulating pad 332 is disposed between the self-aligning block 39 and the radial shoe 33 , and the self-aligning block 39 , the radial insulating pad 332 and the radial shoe 33 are connected as a whole through fasteners. Its structure is simple and compact, and it can effectively isolate the shaft current.

As shown in Figure 20 and Figure 29, the oil supply channel 51 of this embodiment is arranged on the bearing body 36, and the outer ring of the oil supply channel 51 is provided with an annular oil inlet groove 515, and the annular oil inlet groove 515 is connected with the radial shoe oil injection hole 513 It communicates with the thrust shoe oil injection hole 514. The present invention realizes the function that one oil supply source can simultaneously supply oil to each wear-resistant insulating layer through the setting of the annular oil inlet groove 515, and the structure is simple and the oil supply effect is good. While the invention has been described with reference to a preferred embodiment, various modifications may be made and equivalents may be substituted for parts thereof without departing from the scope of the invention. In particular, as long as there is no structural conflict, the technical features mentioned in the various embodiments can be combined in any manner. The present invention is not limited to the specific embodiments disclosed herein, but includes all technical solutions falling within the scope of the claims.

Claims (20)

A bearing assembly for a wind power generator, comprising a rotating shaft connected to the generator rotor, a bearing seat connected to the generator base, and a front bearing part and a rear bearing part arranged between the rotating shaft and the bearing seat, its features In that, both the front bearing component and the rear bearing component are sliding bearings, and the sliding bearing includes a bearing body and a plurality of radial pads, and the plurality of radial pads are arranged at intervals along the inner circumferential direction of the rotating shaft; The inner surface of the radial pad is a radial bearing surface for bearing the radial load of the rotating shaft, and the radial bearing surface is provided with a first wear-resistant insulating layer. The bearing assembly for a wind power generator according to claim 1, wherein the front bearing part and/or the rear bearing part are provided with multiple sets of thrust shoe units, and the number of the thrust shoe units is the same as that of the The number of radial pads is the same, and the thrust pad unit is arranged between adjacent radial pads; each set of thrust pad units includes a thrust pad arranged on the inner end surface of the bearing body, and the thrust pad The outer end surface of the shaft is an axial bearing surface for bearing the axial load of the rotating shaft, and the axial bearing surface is provided with a second wear-resistant insulating layer. The bearing assembly for a wind power generator according to claim 2, wherein a thrust pad mounting block is provided on the inner surface of the bearing body, and the radial pad is limitedly installed between adjacent thrust pad mounting blocks , and the radial bearing surface of the radial pad is higher than the inner surface of the thrust pad mounting block; the thrust pad is installed on one side of the thrust pad mounting block, and the axial bearing of the thrust pad The surface is higher than the end surface of the bearing body. The bearing assembly for a wind power generator according to claim 3, wherein an axial insulating pad is provided between the thrust pad and the thrust pad mounting block, and an axial insulation pad is provided between the radial pad and the bearing body. With radial insulating pads. The bearing assembly for a wind power generator according to any one of claims 2 to 4, wherein the first wear-resistant insulating layer and the second wear-resistant insulating layer are both polytetrafluoroethylene layers or polytetrafluoroethylene layers. Ether ether ketone layer. The bearing assembly for a wind power generator according to any one of claims 2 to 4, further comprising an oil supply channel provided on the front bearing part and the rear bearing part, and the oil supply channel includes radial tile oil injection holes and thrust tile oil injection holes, the ejection ends of the radial tile oil injection holes are arranged between adjacent radial tiles or on the radial tiles; the thrust tile oil injection holes are located on on the thrust pads. The bearing assembly for a wind power generator according to any one of claims 1 to 4, characterized in that the sliding bearing further comprises a housing of the bearing body, a swing adjustment part that ensures the adaptive swing of the bearing body with the rotating shaft, and a limiting The first limiting part of the swing range of the bearing body, wherein the bearing body is swingably installed in the housing of the bearing body through the swing adjusting part, and the first limiting part is arranged at the position of the swing adjusting part . The bearing assembly for a wind power generator according to any one of claims 1 to 4, wherein the sliding bearing further includes an aligning block that ensures the self-adaptive swing of the radial pad along with the rotating shaft, and a limiter for the radial pad. The second limiting part of the swing range, wherein, the self-aligning block is installed on the radial pad, and is located between the radial pad and the bearing body; the outer side of the self-aligning block is provided with The bearing body is oscillatingly fitted with an adjusting spherical surface; the second limiting member is arranged between the self-aligning block and the bearing body. The bearing assembly for a wind power generator according to claims 1 to 4, characterized in that, the rear side of the rear bearing part is provided with a rear bearing oil retaining cavity for providing lubricating oil for the first wear-resistant insulating layer when the oil is cut off , and a sealing assembly that prevents lubricating oil from leaking from the rear side of the rear bearing component to the motor, and the rear bearing oil retention cavity is arranged between the rear bearing component and the sealing assembly. The bearing assembly for a wind power generator according to claim 9, wherein the seal assembly includes an oil deflector ring, an inner seal ring and an outer seal ring, wherein the oil deflector ring is sleeved on the rotating shaft , and can rotate with the rotating shaft; the inner seal ring and the outer seal ring are sequentially sleeved outside the oil deflector ring, and a first seal is left between the inner seal ring and the oil deflector ring There is a second sealing passage between the outer sealing ring and the oil deflector ring; along the radial direction of the rotating shaft, the first sealing passage is located inside the second sealing passage to form a retaining oil steps. The bearing assembly for a wind power generator according to claim 10, wherein a rear bearing oil seal ring is provided on the inner side of the oil deflector ring, and the oil retaining cavity of the rear bearing is composed of the rear bearing oil seal ring, The rear bearing part is enclosed with the rotating shaft; a third sealing channel is provided between the rear bearing oil seal ring and the rotating shaft. The bearing assembly for a wind power generator according to claim 11, wherein the inner side of the oil deflector ring is provided with an annular oil deflector, and the annular oil deflector is surrounded by the rear bearing oil sealing ring to form a The anti-splash area to prevent the lubricating oil from splashing when the rotating shaft rotates. There is an oil gap between the annular oil retaining edge and the rear bearing oil seal ring; the inner upper half of the inner seal ring is provided with an arc The oil edge is along the radial direction of the rotating shaft, and the arc-shaped oil retaining edge is located outside the annular oil retaining edge. The bearing assembly for a wind power generator according to claim 11, wherein a seal is provided in the first sealing passage, the second sealing passage and/or the third sealing passage to prevent part of the lubricating oil from passing through. Protrusion; the height of the sealing protrusion is smaller than the height of the corresponding sealing channel. The bearing assembly for a wind power generator according to claim 11, wherein the lower half of the bearing seat is provided with an oil discharge channel, and the oil inlet end of the oil discharge channel communicates with the inner sealing ring and the The flow space between the oil seal rings of the rear bearing, and the flow space between the inner seal ring and the outer seal ring. The bearing assembly for a wind power generator according to any one of claims 1 to 4, characterized in that, the lower half of the front side of the front bearing component is surrounded by a front bearing oil retaining ring to form a front bearing oil retaining chamber body, the front bearing oil deflecting ring is sleeved on the rotating shaft, the inner surface of the front bearing oil deflecting ring is provided with a sealing protrusion, and there is an overcurrent between the sealing protrusion and the rotating shaft gap. The bearing assembly for a wind power generator according to any one of claims 1 to 4, wherein the sliding bearing further includes multiple sets of limit adjustment units, the radial pads located in the lower half of the bearing body and the The bearing body is in contact, and there is an adjustment gap between the radial pad located on the upper half of the bearing body and the bearing body to prevent the lock-up of the rotating shaft; The limit adjustment unit between the radial shoe and the bearing body remains unchanged, and the adjustment gap shrinks when the rotating shaft expands to contact the radial shoe. The bearing assembly for a wind power generator according to claim 16, wherein the limit adjustment unit includes an elastic adjuster and a shoe limiter, and the elastic adjuster is compressed and arranged at the position of the adjustment gap ; The pad limiter is connected between the radial pad and the bearing body, and a radial pad is provided between the pad limiter and the radial pad or the bearing body Expanded avoidance slot. The bearing assembly for a wind power generator according to claim 17, wherein the elastic adjusting member is a cylindrical spring; the bearing body and the radial pad are correspondingly provided with spring installation grooves to form a spring placement area ; The cylindrical spring is compressed and arranged in the spring placement area. The bearing assembly for a wind power generator according to claim 17, wherein the elastic adjusting member is a disc spring, and the disc spring is limitedly installed at the adjustment gap by a positioning pin; the bearing The body and the radial tile are correspondingly provided with positioning pin installation grooves to form a positioning pin placement area. The bearing assembly for a wind power generator according to claim 17, wherein the pad limiter is a limit screw, and the avoidance groove is provided on the bearing body or the radial pad; when the When the escape groove is set on the bearing body, the tail end of the limit screw is threadedly connected with the radial tile; when the escape groove is arranged on the radial tile, the tail end of the limit screw It is threadedly connected with the bearing body; the head end of the limit screw is limitedly matched with the escape groove under the action of the elastic adjusting member.

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