CN218644648U - Low-heating wind power main shaft bearing - Google Patents

Abstract

The utility model provides a low wind-powered electricity generation main shaft bearing that generates heat, includes inner circle and outer lane, installs two rows of thrust rollers that bear axial load and one row radial roller that bears radial load between inner circle and outer lane, and thrust roller is the toper, and every row of thrust roller satisfies: the central line of the thrust roller, the contact line of the thrust roller and the corresponding thrust inner ring raceway and the contact line of the thrust roller and the corresponding thrust outer ring raceway are jointly intersected at the same point on the bearing rotation axis. The pure rolling between the thrust roller and the thrust roller path can be realized, and a large amount of friction heating caused by sliding motion generated between the thrust roller and the thrust roller path under the action of high load is avoided. In a further preferred scheme, a thrust roller path with convexity is adopted, and the heating of the bearing in the working process can be further reduced by a special structure for installing the roller and the retainer, so that the working reliability of the bearing is ensured.

Description

Low-heating wind power main shaft bearing

Technical Field

The utility model belongs to the technical field of the wind-powered electricity generation bearing, specifically speaking is a wind-powered electricity generation main shaft bearing that generates heat lowly.

Background

Wind power generation is an important way for developing and utilizing clean and environment-friendly renewable energy sources. In recent years, wind power equipment technology is rapidly developed, and installed capacity is continuously increased.

In a direct-drive wind generating set, a main shaft bearing is a loaded supporting part of key machinery (a main shaft system) in the wind generating set, and the main shaft bearing has extremely high reliability requirement within the service life of 20 years because the wind generating set is difficult to hoist and maintain, and the running performance of the main shaft bearing of the wind generating set is increasingly emphasized. In the existing wind turbine generators of different types, the bearing structure for supporting the main shaft system has various types, and the three-row roller bearing has the advantages of bearing performance and processing manufacturability, so that the bearing structure is a main shaft bearing structure form with application potential in the wind turbine generators for directly driving the wind turbine generators.

The structure of a three-row roller bearing in the prior art is shown in fig. 1: the thrust roller bearing mainly comprises an outer ring 4a, a main thrust inner ring 1a and an auxiliary thrust inner ring 9a which are arranged inside the outer ring, a main thrust roller 3a, an auxiliary thrust roller 8a and a radial roller 5a which are arranged between the outer ring 4a and the two inner rings, and a main thrust retainer 2a, an auxiliary thrust retainer 7a and a radial retainer 6a which are arranged corresponding to each row of rollers and used for maintaining the rollers to be uniformly distributed along the circumference of the bearing. The main thrust roller 3a and the auxiliary thrust roller 8a are arranged perpendicular to the rotation central axis of the bearing, are important bearing rolling elements in the three-row roller bearing, and resist the action of axial load and moment load from the wind wheel in the use and rotation process of the three-row roller bearing.

In the prior art, the main thrust roller 3a, the auxiliary thrust roller 8a and the radial roller 5a in the three-row roller bearing all adopt cylindrical rollers, and for the main thrust roller 3a and the auxiliary thrust roller 8a, because the circumferential radiuses of raceways at the positions of two ends of the rollers are different, the circumferential perimeters of the corresponding raceways are also different, so that the outer end of the roller lags behind the inner end of the roller in the revolution process of the roller, and the roller tends to be skewed.

In the prior art, in order to restrain the thrust rollers, the assembly of the outer surfaces of the rollers and the inner surfaces of the pockets of the corresponding cages is in a contact limited state, so that the cages maintain the correct postures of the rollers by forcing the sliding of the two ends of the rollers relative to the raceways. Under the action of wind load, the contact load between a single roller and the raceway reaches hundreds of thousands of newtons, and when the bearing continuously rotates in a wind turbine generator host, continuous sliding motion between the roller and the raceway under the action of high load causes a large amount of friction heating, so that the temperature of the bearing is raised too high.

In addition, in the existing three-row roller wind power main shaft bearing, the surfaces of the pockets of the retainer are in contact with the outer cylindrical surface of the rollers, and the rollers are kept uniformly distributed in the circumferential direction of the bearing by restraining the outer cylindrical surface of the rollers. Specifically, the rollers are fitted in the pockets of the respective cages, and during the rotation of the bearing, a large area of sliding frictional contact exists between the outer cylindrical surface of the rollers and the inner surface of the pockets, which also causes the bearing to generate heat.

Furthermore, in the three-row roller bearing in the prior art, in order to realize the positioning of the retainer in the raceway cavity, a large amount of sliding friction between the retainer and the raceway also causes the heating and temperature rise of the bearing.

In a word, a large amount of sliding contact friction in the three-row roller wind power main shaft bearing in the prior art is a source of overhigh bearing temperature rise, and further changes of the matching state of the bearing and deterioration of mechanical property, shortens the service life of the bearing and even causes burning loss of the bearing due to temperature rise and thermal expansion. There is therefore a need for an improved roller bearing arrangement that solves the above problems.

SUMMERY OF THE UTILITY MODEL

The utility model aims at providing a low wind-powered electricity generation main shaft bearing that generates heat.

In order to realize the purpose, the utility model discloses the technical scheme who adopts is: the utility model provides a low wind-powered electricity generation main shaft bearing that generates heat, includes inner circle and outer lane, installs two rows of thrust rollers that bear axial load and one row radial roller that bears radial load between inner circle and outer lane, its characterized in that: the thrust rollers are all conical, and each row of thrust rollers meet the following requirements: the central line of the thrust roller, the contact line of the thrust roller and the corresponding thrust inner ring raceway and the contact line of the thrust roller and the corresponding thrust outer ring raceway are jointly intersected at the same point on the bearing rotation axis.

Preferably, the raceway surface of the thrust inner ring corresponding to each row of thrust rollers is an outer tapered surface, and the raceway surface of the thrust outer ring corresponding to each row of thrust rollers is a plane.

Furthermore, the generatrices of the thrust inner ring raceway and the thrust outer ring raceway corresponding to each row of thrust rollers are designed with convexity, and the convexity is high in the middle and low in two ends in the radial direction.

Furthermore, each row of thrust rollers are arranged between the inner ring and the outer ring through the thrust retainer, each thrust retainer comprises an inner ring and an outer ring, lintel columns which are uniformly distributed along the circumference are connected between the inner ring and the outer ring, a thrust roller mounting window hole is formed between every two adjacent lintel columns, each thrust roller is arranged in the corresponding thrust roller mounting window hole, two ends of each thrust roller are respectively provided with a thrust roller positioning pin, one end of each thrust roller positioning pin is provided with a spherical surface which is assembled with a spherical socket-shaped counter bore arranged at the end part of each thrust roller, the other end of each thrust roller positioning pin is provided with a threaded section, the thrust roller inner positioning pin positioned on the inner side is connected with a threaded hole of the inner ring through the threaded section, and the thrust roller outer positioning pin positioned on the outer side is connected with a threaded hole of the outer ring through the threaded section.

Furthermore, the thread bottom diameter of the thread section of the positioning pin in the thrust roller is larger than the diameter of the adjacent optical axis section,

the tail end of the thread section is provided with a step head; the crest diameter of the thread section of the thrust roller outer positioning pin is smaller than the diameter of the adjacent optical axis section, so that an assembling and pressing positioning step is formed between the thread section of the thrust roller outer positioning pin and the adjacent optical axis section.

Furthermore, one end of the lintel column is provided with an optical axis section assembled with the light hole on the outer ring, the other end of the lintel column is provided with a thread section assembled with the corresponding thread hole on the inner ring, and the tail end of the thread section is provided with a limit head part with the diameter larger than the diameter of the thread top of the thread section.

Furthermore, flanges are arranged on two sides of the thrust inner ring raceway corresponding to each row of thrust rollers, so that the thrust rollers are positioned along the radial direction of the bearing.

Preferably, the radial retainer for mounting the radial roller comprises an upper ring and a lower ring, radial lintel columns which are uniformly distributed along the circumference are connected between the upper ring and the lower ring, a radial roller mounting window hole is formed between two adjacent radial lintel columns, the radial roller is arranged in the radial roller mounting window hole, two ends of the radial roller are respectively provided with a radial roller positioning pin, one end of each radial roller positioning pin is provided with a spherical surface which is assembled with a spherical socket-shaped counter bore arranged at the end part of the radial roller, the other end of each radial roller positioning pin is provided with a threaded section, the upper radial roller mounting positioning pin positioned above is connected with a threaded hole of the upper ring through the threaded section, and the lower radial roller mounting positioning pin positioned below is connected with a threaded hole of the lower ring through the threaded section.

Has the beneficial effects that:

(1) The utility model discloses in, thrust roller adopts the toper, and thrust roller's central line, thrust roller and thrust inner circle raceway's contact wire, thrust roller and thrust outer lane raceway's contact wire cross on the bearing axis of revolution jointly, can realize the pure roll between thrust roller and the thrust raceway from this, has avoided producing under the high load effect between thrust roller and the thrust raceway that a large amount of frictions that sliding motion leads to generate heat.

(2) The raceway surface of the thrust inner ring raceway is set as an outer conical surface, and the raceway surface of the thrust outer ring raceway is set as a plane vertical to the rotation axis of the bearing, so that the thrust outer ring raceway has no limitation on relative radial displacement between the inner ring and the outer ring under the action of radial load, and the thrust roller is prevented from interfering the radial load borne by the radial roller; moreover, the structure is more convenient to process and manufacture, and has great process convenience.

(3) In a further preferred scheme, the generatrix of the thrust inner ring raceway and the thrust outer ring raceway is designed into a structure with convexity, so that the contact between two ends of a thrust roller and the raceways is avoided, the stress concentration and early fatigue failure of the raceway surface at the contact part of the end part can be avoided, and the contact line length of the thrust roller and the deformation heating of the circular elastic contact are reduced.

(4) In the design of the roller and retainer installation component, through the assembly structure between the spherical ball socket-shaped counter bore at the end part of the roller and the spherical working end of the roller positioning pin, and the flanges are arranged on two sides of the roller path, not only is the function of circumferential uniform distribution and restriction of the retainer on the roller realized, but also the positioning of the retainer in a roller path cavity is realized, and the friction between the rolling surfaces of the retainer and the roller and between the flange surfaces of the retainer and the roller path is avoided, thereby reducing the area of the sliding friction contact surface between the retainer and the roller to the maximum extent, and reducing the heat generation in the working process of the bearing. In addition, the lintel column in the retainer adopts a cylindrical structure, which is very beneficial to the flow and friction heat dissipation of lubricating grease.

(6) The utility model discloses a special mounting structure has been adopted with the installation component of roller to the holder, simultaneously because the roller adopts the flange to fix a position, holder and raceway die cavity periphery all contactless, is showing and is reducing occuping of raceway die cavity space to can reduce the hindrance effect of lubricating grease to the holder revolution, reduce the friction between holder and the lubricating grease and generate heat, in addition the utility model discloses a reduction of holder volume also brings the reduction of weight, thereby has also reduced the holder and has generated heat because the friction that gravity load caused.

Drawings

Fig. 1 is a schematic view of a three-row roller wind power main shaft bearing structure in the prior art.

Fig. 2 is a schematic structural diagram of the present invention.

Fig. 3 is a schematic view of the structure of the convexity of the thrust raceway.

Fig. 4 is a schematic view of an assembly structure of the thrust roller and the thrust retainer.

Fig. 5 is a schematic view of a thrust roller structure.

Fig. 6 is a schematic structural view of the thrust retainer.

Fig. 7 is a schematic view of a positioning pin structure in the thrust roller.

Fig. 8 is a schematic view of a thrust roller outer dowel pin configuration.

Fig. 9 is a lintel column.

FIG. 10 is a view showing an assembly structure of radial rollers and radial cages

Fig. 11 is a radial cage.

Fig. 12 is a radial lintel column.

The labels in the figure are: 1. the thrust roller bearing comprises a main thrust inner ring, 101, a thrust inner ring raceway, 102, a flange, 2, a main thrust retainer, 21, an inner ring, 22, an outer ring, 23, a thrust roller inner positioning pin, 231, a spherical surface, 232, a threaded section, 233, a step head, 234, a straight groove, 24, a thrust roller outer positioning pin, 242, an assembly pressing positioning step, 25, a lintel column, 251, a smooth shaft section, 252, a positioning step, 253, a threaded connection section, 254, a limit head, 3, a main thrust roller, 4, an outer ring, 401, a thrust outer ring raceway, 5, a radial roller, 6, a radial retainer, 61, an upper ring, 62, a lower ring, 63, a radial roller positioning pin, 64, a radial lintel column, 641, a radial smooth shaft section, 642, a connection positioning section, 643, a radial threaded section, 7, an auxiliary thrust retainer, 8, an auxiliary thrust roller, 9 and an auxiliary thrust inner ring.

Detailed Description

The following detailed description of the present invention is provided with reference to the accompanying drawings and examples, but not to be construed as limiting the present invention in any way.

The terms "inner" and "outer" are used herein as the same as the corresponding figures, and are only for convenience of description, and do not limit the scope of the present invention.

The main thrust inner ring and the auxiliary thrust inner ring in terms of main thrust inner ring, auxiliary thrust inner ring and the like refer to that an inner ring bearing the thrust load action of a windward turbine is the main thrust inner ring, a corresponding roller is a main thrust roller, and a corresponding retainer is a main thrust retainer after a bearing is installed in a wind turbine; the other is the auxiliary thrust inner ring and the auxiliary thrust roller, and the auxiliary thrust retainer, namely the main thrust retainer and the auxiliary thrust roller, does not form the limitation of the bearing structure per se.

Referring to fig. 2, the low-heat-generation wind power main shaft bearing comprises an inner ring and an outer ring 4, wherein two rows of thrust rollers bearing axial load and one row of radial rollers 5 bearing radial load are arranged between the inner ring and the outer ring 4.

In the embodiment shown in fig. 2, the inner ring comprises a main thrust inner ring 1 and an auxiliary thrust inner ring 9, and the bearing assembly and the processing of the thrust inner ring raceway and the radial raceway are facilitated by adopting a mode that the two inner ring parts are manufactured separately and then combined into an integral inner ring.

In this embodiment, referring to fig. 2, two rows of thrust rollers, namely the main thrust roller 3 and the auxiliary thrust roller 8, are tapered, and the structure of each row of thrust rollers satisfies the following conditions: the central line of the thrust roller, the contact line of the thrust roller and the corresponding thrust inner ring raceway and the contact line of the thrust roller and the corresponding thrust outer ring raceway are converged at the same point on the bearing rotation axis. Therefore, pure rolling between the thrust roller and the corresponding thrust roller path can be realized in the working process of the bearing, and a large amount of friction heating caused by sliding motion generated between the thrust roller and the corresponding thrust roller path under the action of high load is avoided.

In order to implement the above technical solution, the specific implementation manner adopted may be that the raceway surface of the thrust inner ring corresponding to each row of thrust rollers is an outer conical surface, and the raceway surface of the thrust outer ring corresponding to each row of thrust rollers is a plane; the tapered surface may be provided in the thrust outer ring raceway on the outer ring and the flat surface may be provided in the corresponding thrust inner ring raceway, but the former is preferred because the processing is more convenient than the latter.

By adopting the preferred embodiment, interference of the thrust rollers on the thrust outer ring raceway on radial load borne by the radial rollers can be avoided. Thereby ensuring the bearing to work normally and reliably.

In the preferred embodiment, the generatrix of the thrust inner ring raceway and the thrust outer ring raceway corresponding to each row of thrust rollers is designed with convexity, i.e. the generatrix is in a shape gradually protruding from two ends to the middle in the radial direction, and is similar to a waist drum generatrix. As for the thrust inner ring raceway 101, although it has convexity, it is a tapered surface having a large end and a small end as a whole.

For the thrust outer ring raceway 401, the convexity of the generatrix is the same, so that the contact lines of all the generatrixes of the thrust outer ring raceway 401 and the corresponding thrust rollers are in the same plane, i.e. the contact surface of the thrust outer ring raceway and the thrust rollers is still a plane.

The technical characteristics can avoid stress concentration and early fatigue failure of the raceway surface at the contact part of the end part of the thrust roller and the thrust raceway, and reduce the length of the contact line of the thrust roller and the corresponding thrust raceway, thereby reducing deformation heating of circular elastic contact, and the structure is easy to process.

As shown in fig. 2 and fig. 3, in this embodiment, each row of thrust rollers, i.e., the main thrust roller 3 and the auxiliary thrust roller 8, are mounted between the inner ring and the outer ring through their own thrust retainers, and the thrust retainers are mounted in corresponding raceway cavities.

As shown in fig. 2, the radial roller and radial cage assembly (fig. 10) is assembled in a radial raceway cavity formed between the bearing inner and outer races. Specifically, in this embodiment, the main thrust inner ring 1 and the auxiliary thrust inner ring 9 are connected at the lower edge of the radial raceway cavity, the radial roller rolls in the radial inner ring raceway and the radial outer ring raceway, and flanges are also provided on both sides of the radial inner ring raceway to position the roller along the axial direction of the bearing (the specific structure is similar to the arrangement of the flanges of the thrust inner ring raceway 101, and refer to the arrangement of the flanges of the thrust inner ring raceway 101 in fig. 3).

As shown in fig. 4 to 6, the structure of the thrust cage will be described by taking the main thrust cage 2 as an example. The thrust retainer comprises an inner ring 21 and an outer ring 22, lintel columns 25 which are uniformly distributed along the circumference are connected between the inner ring 21 and the outer ring 22, a thrust roller mounting window hole is formed between two adjacent lintel columns, and a thrust roller is arranged in the thrust roller mounting window hole.

Specifically, two thrust roller positioning pins are respectively arranged at two ends of each thrust roller, and the thrust rollers are installed in a matching manner with the inner ring 21 and the outer ring 22 of the thrust retainer through the two thrust roller positioning pins.

The thrust roller positioning pins are structurally shown in fig. 7 and 8, spherical surfaces 231 are arranged at one ends of the two thrust roller positioning pins and are matched with spherical-socket-shaped counter bores 32 arranged at the end parts of the thrust rollers, and threaded sections 232 are arranged at the other ends of the thrust roller positioning pins.

The inner thrust roller locating pin 23 on the inner side is connected with a corresponding threaded hole on the inner ring 21 through a threaded section, and the outer thrust roller locating pin on the outer side is connected with a threaded hole on the outer ring 22 through a threaded section.

As shown in fig. 7, the thread root diameter of the positioning pin 23 in the thrust roller is larger than the diameter of the adjacent smooth shaft section, a stepped head 233 is provided at the end of the thread section, and a straight groove 234 for screwing the guide pin in cooperation with the screwdriver is provided on the end surface of the stepped head 233.

As shown in fig. 8, the crest diameter of the threaded section of the thrust roller outer locating pin 24 is smaller than the diameter of the adjacent stub shaft section, so that a fitting pressing locating step 242 is formed between the threaded section of the thrust roller outer locating pin and the adjacent stub shaft section.

As shown in fig. 9, in the present embodiment, the lintel column 25 is provided with an optical axis segment 251 fitted with the optical hole on the outer ring 22 at one end, a threaded segment 253 fitted with the corresponding threaded hole on the inner ring 21 at the other end, and a limit head 254 with a diameter larger than the crest diameter of the threaded segment 253 is provided at the end of the threaded segment 253.

In order to facilitate the installation and positioning of the lintel column 25 and the outer ring 22, a transition section with a diameter larger than that of the optical axis section 251 is provided between the optical axis section 251 and the threaded section 253 (the diameter of the transition section is smaller than the root diameter of the threaded section 253), so that a positioning step 252 is formed between the transition section and the optical axis section 251.

In the assembling structure of the thrust retainer and the thrust roller, because the two ends of the thrust roller are correspondingly installed with the inner ring and the outer ring of the thrust retainer through the spherical-socket-shaped counter bores and the corresponding positioning pins, in the working process of the bearing, the contact area between the thrust roller and the corresponding positioning pins is small, the thrust roller and the corresponding positioning pins are in spherical contact, the thrust roller and the corresponding positioning pins can relatively rotate, the relative friction is small, and therefore the heat productivity is greatly reduced. The thrust roller drives the thrust retainer to perform revolution motion in the revolution process. The thrust retainer does not contact with the corresponding track surface, so that heat cannot be generated due to relative sliding, and the heat generation amount of the bearing is further reduced on the whole.

When the installation is carried out, the thrust roller outer positioning pin 24 is correspondingly screwed into the corresponding threaded hole of the outer ring 22, the thrust roller is placed in the thrust roller outer positioning pin, the thrust roller inner positioning pin 23 is placed in the inner ring, the thrust roller inner positioning pin penetrates out of the corresponding threaded hole on the inner ring 21, the working end of the spherical surface of the thrust roller inner positioning pin is matched and installed with the spherical socket-shaped counter bore of the thrust roller, and the position of the thrust roller in the thrust retainer can be controlled and adjusted by adjusting the positions of the two thrust roller positioning pins so as to meet the preset requirement. Outer locating pins 24 are equispaced on the outer ring 22.

Finally, the inner ring 21 and the outer ring 22 are fixedly connected by the lintel column 25, specifically, the lintel column 25 can penetrate out of a corresponding threaded hole on the inner ring 21 and then be inserted into an unthreaded hole in the outer ring 22 to be installed in a clearance fit with the unthreaded hole (the lintel column 25 is also uniformly distributed along the inner ring 21 and the outer ring 22), and after the inner ring and the outer ring are adjusted to be coaxial, the lintel column 25 and the outer ring 22 are fixedly connected by welding. (because one end of the lintel column 25 is provided with the threaded section, and the other end is provided with the positioning step 252, after the matching position of the threaded section and the inner ring is adjusted, the outer ring is positioned by using the positioning step 252, that is, the lintel column and the outer ring do not need to be welded and fixed, so that the detachable assembly effect is realized).

The flange is adopted to radially position the thrust roller along the bearing, so that the whole thrust roller and the thrust retainer assembly are radially positioned, compared with the prior art that the retainer is directly contacted with the inner ring and the outer ring to position, the positioning contact surface is reduced, the heat productivity generated by relative friction motion in the working process of the bearing can be further reduced, and in the same way, the flange is adopted to axially position the radial roller and also has the effect of reducing the heat generation of the bearing.

As shown in fig. 10 and 11, in this embodiment, the radial retainer 6 for mounting the radial roller 5 includes an upper ring 61 and a lower ring 62, radial lintel posts 64 uniformly distributed along the circumference are connected between the upper ring 61 and the lower ring 62, a radial roller mounting window hole is formed between two adjacent radial lintel posts, the radial roller 5 is disposed in the radial roller mounting window hole, two ends of the radial roller 5 are respectively provided with a radial roller positioning pin 63, one end of the radial roller positioning pin is provided with a spherical surface which is fitted with a spherical socket-shaped counter bore provided at the end of the radial roller, the other end of the radial roller positioning pin is provided with a threaded section, the upper positioning pin of the upper radial roller is connected with the threaded hole of the upper ring through the threaded section, and the lower positioning pin of the lower radial roller is connected with the threaded hole of the lower ring through the threaded section.

The radial threaded pin may be configured as a thrust roller outer locating pin as shown in fig. 8.

The specific mounting of the radial rollers in the radial cage 6 may be by a similar mounting arrangement to the thrust roller and thrust cage assembly, with only some differences in the arrangement of the radial lintel column 64 and the lintel column 25.

As shown in fig. 12, the radial cross beam column 64 has a radial spindle section 641 and a radial threaded section 643, and a connection positioning section 642 having a larger diameter than the radial spindle section 641 and the radial threaded section 643 is provided between the radial spindle section 641 and the radial threaded section 643. The radial lintel column 64 has no directionality in the installation of the upper ring and the lower ring, and can be connected with the upper ring 61 in a threaded manner at the upper end and the lower ring 62 in a welded manner at the other end, or can be connected with the lower ring in a threaded manner at the lower end and the upper end is connected with the upper ring in a welded manner. The radial limitation in the radial optical axis section and the radial threaded section in the section is only used for distinguishing the threaded section and the optical axis of other parts, and the structure is not limited by the radial limitation.

In the working process of the bearing, because the radial rollers 5 are axially positioned by the flanges arranged at the two sides of the radial raceway, the radial rollers 5 perform revolution motion around the bearing revolution axis in the radial inner ring raceway and the radial outer ring raceway besides rolling and rotating around two guide pins surrounding the radial rollers, and the radial rollers guide the revolution motion of the radial retainer 6 while revolving. Since there is no contact between the radial cage 6 and the corresponding raceway surface, heat generation due to relative sliding does not occur, and the heat generation amount of the bearing as a whole is further reduced.

In this embodiment, the lintel column 25 and the radial lintel column 64 are both cylindrical structures, and there is a gap between them and the corresponding roller, so that the flow of grease and frictional heat dissipation are also greatly facilitated.

Parts not described in detail herein are prior art.

The above embodiments are only used for illustrating the technical solutions of the present invention and not for limiting the same, and it should be understood by those of ordinary skill in the art that the embodiments of the present invention can be modified or replaced with equivalents with reference to the above embodiments, and any modifications or equivalent substitutions which do not depart from the spirit and scope of the present invention are intended to be covered by the claims which are appended hereto.

Claims (8)

1. The utility model provides a low wind-powered electricity generation main shaft bearing that generates heat, includes inner circle and outer lane, installs two rows of thrust rollers that bear axial load and one row radial roller that bears radial load between inner circle and outer lane, its characterized in that: the thrust rollers are all conical, and each row of thrust rollers meet the following requirements: the central line of the thrust roller, the contact line of the thrust roller and the corresponding thrust inner ring raceway and the contact line of the thrust roller and the corresponding thrust outer ring raceway are jointly intersected at the same point on the bearing rotation axis.

2. The low-heat-generation wind power main shaft bearing according to claim 1, characterized in that: the raceway surface of the thrust inner ring corresponding to each row of thrust rollers is an outer conical surface, and the raceway surface of the thrust outer ring corresponding to each row of thrust rollers is a plane.

3. The low-heat generation wind power main shaft bearing according to claim 1 or 2, characterized in that: the generatrix of the thrust inner ring raceway and the thrust outer ring raceway corresponding to each row of thrust rollers is designed with convexity which is convex in the radial direction with a high middle part and low two ends.

4. The low-heat-generation wind power main shaft bearing according to claim 1 or 2, characterized in that: each row of thrust rollers are arranged between the inner ring and the outer ring through a thrust retainer, each thrust retainer comprises an inner ring (21) and an outer ring (22), lintel columns (25) which are uniformly distributed along the circumference are connected between the inner ring and the outer ring, a thrust roller mounting window hole is formed between every two adjacent lintel columns, each thrust roller is arranged in the corresponding thrust roller mounting window hole, two thrust roller positioning pins are respectively arranged at two ends of each thrust roller, a spherical surface is arranged at one end of each thrust roller positioning pin and assembled with spherical socket-shaped counter bores arranged at the end parts of each thrust roller, a threaded section is arranged at the other end of each thrust roller positioning pin, the thrust roller inner positioning pin (23) positioned on the inner side is connected with a threaded hole of the inner ring (21) through the threaded section, and the thrust roller outer positioning pin (24) positioned on the outer side is connected with a threaded hole of the outer ring (22) through the threaded section.

5. The low-heat-generation wind power main shaft bearing according to claim 4, characterized in that: the diameter of the thread bottom of the threaded section of the positioning pin (23) in the thrust roller is larger than that of the adjacent optical axis section, and the tail end of the threaded section is provided with a step head; the thread crest diameter of the thread section of the thrust roller outer positioning pin is smaller than the diameter of the adjacent optical axis section, so that an assembling and pressing positioning step is formed between the thread section of the thrust roller outer positioning pin and the adjacent optical axis section.

6. The low-heat-generation wind power main shaft bearing according to claim 4, characterized in that: one end of the lintel column (25) is provided with an optical axis section assembled with the light hole on the outer ring, the other end is provided with a thread section assembled with the corresponding thread hole on the inner ring, and the tail end of the thread section is provided with a limit head part with the diameter larger than the diameter of the thread top of the thread section.

7. The low-heat-generation wind power main shaft bearing according to claim 4, characterized in that: and flanges are arranged on two sides of the thrust inner ring raceway corresponding to each row of thrust rollers, so that the thrust rollers are positioned along the radial direction of the bearing.

8. The low-heat-generation wind power main shaft bearing according to claim 1 or 2, characterized in that: the radial retainer for mounting the radial roller comprises an upper ring (61) and a lower ring (62), radial lintel posts (64) which are uniformly distributed along the circumference are connected between the upper ring and the lower ring, a radial roller mounting window hole is formed between every two adjacent radial lintel posts, the radial roller is arranged in the radial roller mounting window hole, two ends of the radial roller are respectively provided with a radial roller positioning pin, one end of each radial roller positioning pin is provided with a spherical surface which is assembled with a spherical socket-shaped counter bore arranged at the end part of the radial roller, the other end of each radial roller positioning pin is provided with a threaded section, the upper positioning pin of the radial roller positioned above is connected with a threaded hole of the upper ring (61) through the threaded section, and the lower positioning pin of the radial roller positioned below is connected with a threaded hole of the lower ring (62) through the threaded section.

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