Tapered roller bearing, shafting structure and wind generating set
The tapered roller bearing with multiple rows of smaller elements addresses the challenges of large loads in wind turbines by enhancing load-bearing capacity and reducing production and assembly difficulties, leading to cost-effective and lightweight wind turbines.
Patent Information
- Application Number
- CN202323599051.4
- Authority / Receiving Office
- CN · China
- Patent Type
- Utility models(China)
- Current Assignee / Owner
- Filing Date
- 2023-12-27
- Publication Date
- 2024-12-10
- Estimated Expiration
- 2033-12-27
AI Technical Summary
Large-scale wind turbines face challenges with increasing loads, leading to larger bearing diameters, higher production and assembly difficulties, increased costs, and higher probabilities of sliding and tilting due to oversized rolling elements, which also increase the weight and transportation costs of wind turbines.
A tapered roller bearing design with at least two rows of smaller-sized rolling elements, each row facing the large diameter end of the inner ring, distributing the load and maintaining a similar diameter, thereby reducing manufacturing and assembly difficulties while enhancing load-bearing capacity.
The design reduces the probability of sliding and tilting, decreases the size of the transmission chain, lowers overall costs, and facilitates transportation by maintaining a smaller diameter, thus optimizing the wind turbine's weight and cost.
Smart Images
Figure CN222141787U_ABST
Abstract
Description
Technical Field
[0001] The utility model relates to the field of wind power generation, in particular to a tapered roller bearing, a shaft system structure and a wind power generator set. Background Art
[0002] With the development of large-scale wind turbines, the power of the units is gradually increasing, and the load on the units is also increasing. The main bearing is the main component that bears the wind load in the wind turbine. In order to meet the large load requirements, the diameter of the bearing is also gradually increasing. Figure 1 As shown, it consists of four parts: outer ring 140a, inner ring 110a, rolling element 130a and retaining frame 120a. In order to bear large loads, rolling element 130a needs to be thicker and longer, which will make the production and manufacturing of rolling element 130a more difficult and increase the difficulty of bearing assembly. Moreover, if rolling element 130a is too large, it will increase the probability of sliding and tilting during the operation of the bearing, which is easy to accelerate the damage of the bearing. Moreover, the increase in the size of rolling element 130a will lead to the increase in the size of outer ring 140a, which will in turn lead to the increase in the size of the transmission chain matching the bearing, which will cause the overall cost of the wind turbine to be higher, the weight to be heavier, and increase the transportation cost. Utility Model Content
[0003] Therefore, the purpose of the present invention is to provide a tapered roller bearing, a shaft system structure and a wind turbine generator set to at least solve one of the problems existing in the above-mentioned prior art or related technology.
[0004] The first aspect of the utility model provides a tapered roller bearing, which includes: an inner ring and an outer ring that are coaxially sleeved and correspond to each other, the inner ring having a large diameter end and a small diameter end that are opposite to each other in its own axial direction; at least two retaining frames that are arranged on a raceway formed between the inner ring and the outer ring and distributed along the axial direction of the inner ring; at least two rows of rolling elements, at least two rows of rolling elements are installed on at least two retaining frames in a one-to-one manner, each row of rolling elements includes a plurality of tapered rollers distributed circumferentially, and the large diameter ends of the plurality of tapered rollers of each row of rolling elements are all facing the large diameter end of the inner ring.
[0005] The tapered roller bearing provided by the embodiment of this aspect has at least two retainers arranged axially between a pair of inner rings and outer rings, and a row of rolling elements is arranged in each retainer, so that the large diameter ends of the tapered rollers in at least two rows of rolling elements are all facing the large diameter end of the inner ring. Compared with the related art in which there is only one row of rolling elements between the inner ring and the outer ring, and the rolling elements are larger in size, the present embodiment can replace the single row of large-sized rolling elements with the load by distributing the load by at least two rows of rolling elements, so that the bearing can be equipped with smaller-sized rolling elements, and by increasing the number of rows of rolling elements, the bearing can achieve a large load-bearing capacity with the diameter unchanged or slightly changed. This not only eliminates the problems of greater difficulty in production and assembly caused by large-sized tapered rollers, but also reduces the probability of tapered rollers sliding and skewing when the bearing is running, thereby increasing the service life of the bearing. In addition, when tapered roller bearings are used as the main bearings of wind turbines, even if the load is large, the size of the matching transmission chain will not increase too much because the diameter of the tapered roller bearings does not change much. This helps to reduce the overall cost of the wind turbine, reduce the weight of the unit, and facilitate transportation.
[0006] The second aspect of the utility model provides a shaft system structure for a wind turbine generator set, wherein the shaft system structure includes a moving shaft, a fixed shaft, and a first bearing and a second bearing located between the moving shaft and the fixed shaft. One end of the moving shaft is used to be connected to a wheel hub, and the first bearing and the second bearing are distributed at both ends of the moving shaft. The bearing close to the wheel hub among the first bearing and the second bearing is a tapered roller bearing as described in the first aspect of the utility model.
[0007] The shaft system structure provided by the embodiment of this aspect has the tapered roller bearing provided by the embodiment of the first aspect, and thus has the beneficial effects of the embodiment of the first aspect, which will not be described in detail here. Moreover, the load borne by the bearing close to the hub of the shaft system structure is relatively large, so the bearing is the tapered roller bearing provided by the embodiment of the first aspect, which can bear a large load without significantly increasing the bearing diameter, which is conducive to meeting the requirements of the current high-power wind turbine generator set.
[0008] A third aspect of the present invention provides a wind turbine generator set, comprising the shaft system structure as described in the second aspect of the present invention.
[0009] The wind turbine generator set provided by the embodiment of this aspect has the shaft system structure provided by the embodiment of the second aspect, and thus has the beneficial effects of the embodiment of the second aspect, which will not be described in detail here.
[0010] Other aspects and / or advantages of the general inventive concept will be partially set forth in the following description, and some will be clear from the description or may be learned through implementation of the general inventive concept. BRIEF DESCRIPTION OF THE DRAWINGS
[0011] The above and other objects and features of the present invention will become more apparent through the following description in conjunction with the accompanying drawings which exemplarily illustrate an example, in which:
[0012] Figure 1 A cross-sectional schematic diagram of a tapered roller bearing according to an embodiment of the related art is shown;
[0013] Figure 2 A schematic structural diagram of a tapered roller bearing according to an embodiment of the present application is shown;
[0014] Figure 3 A schematic cross-sectional view of a tapered roller bearing according to an embodiment of the present application is shown;
[0015] Figure 4 Shows Figure 3 A local enlarged schematic diagram of point I in the middle;
[0016] Figure 5 An exploded schematic diagram of a tapered roller bearing according to an embodiment of the present application is shown;
[0017] Figure 6 A partial structural schematic diagram of a shaft system structure of an embodiment of the present application is shown.
[0018] Figure 1 Description of reference numerals:
[0019] 110a inner ring, 120a cage, 130a rolling element, 140a outer ring;
[0020] Figures 2 to 6 Description of reference numerals:
[0021] 110 inner ring, 120 retaining frame, 130 rolling elements, 131 first row of rolling elements, 132 second row of rolling elements, 140 outer ring, 150 retaining ring, 20 moving shaft, 30 fixed shaft, 40 first bearing, 50 second bearing. DETAILED DESCRIPTION
[0022] The following specific embodiments are provided to help the reader obtain a comprehensive understanding of the methods, devices and / or systems described herein. However, after understanding the disclosure of the present application, various changes, modifications and equivalents of the methods, devices and / or systems described herein will be clear. For example, the order of operations described herein is only an example and is not limited to those orders set forth herein, but can be changed as will be clear after understanding the disclosure of the present application, except for operations that must occur in a specific order. In addition, for greater clarity and simplicity, the description of features known in the art may be omitted.
[0023] The features described herein can be implemented in different forms and should not be construed as being limited to the examples described herein. Rather, the examples described herein have been provided to illustrate only some of the many possible ways to implement the methods, devices, and / or systems described herein, which will be clear after understanding the disclosure of the present application.
[0024] As used herein, the term "and / or" includes any one of the associated listed items and any combination of any two or more.
[0025] Although terms such as "first", "second", and "third" may be used herein to describe various members, components, regions, layers, or portions, these members, components, regions, layers, or portions should not be limited by these terms. Instead, these terms are only used to distinguish one member, component, region, layer, or portion from another member, component, region, layer, or portion. Therefore, without departing from the teachings of the examples described herein, the first member, first component, first region, first layer, or first portion referred to in the examples may also be referred to as the second member, second component, second region, second layer, or second portion.
[0026] In the specification, when an element such as a layer, a region or a substrate is described as being “on”, “connected to” or “coupled to” another element, the element may be directly “on”, “connected to” or “coupled to” another element, or one or more other elements may be present therebetween. Conversely, when an element is described as being “directly on”, “directly connected to” or “directly coupled to” another element, other elements may not be present therebetween.
[0027] The terms used herein are only used to describe various examples and are not intended to limit the disclosure. Unless the context clearly indicates otherwise, the singular form is also intended to include the plural form. The terms "comprise", "include" and "have" indicate the presence of the described features, quantities, operations, components, elements and / or combinations thereof, but do not exclude the presence or addition of one or more other features, quantities, operations, components, elements and / or combinations thereof. The term "plurality" represents any number of two and more than two.
[0028] The limitations of directional terms such as "above" and "below" in this application are based on the directional limitations of the product in normal use, unless otherwise specified.
[0029] Unless otherwise defined, all terms used herein, including technical terms and scientific terms, have the same meanings as those generally understood by ordinary technicians in the field to which the present invention belongs after understanding the present invention. Unless explicitly defined as such herein, terms such as those defined in general dictionaries should be interpreted as having meanings consistent with their meanings in the context of the relevant field and the present invention, and should not be interpreted in an idealized or overly formal way.
[0030] The main bearings of wind turbines in related technologies are mostly single-row tapered roller bearings, such as Figure 1 As shown, there is a single-row rolling element 130a. Two single-row tapered roller bearings are installed back-to-back on the shaft structure to bear the weight of the impeller and the wind load. As the power of the wind turbine generator set gradually increases and the load increases, the diameter of the single-row tapered roller bearing also needs to increase, which leads to an increase in the size of the transmission chain of the unit matched therewith, an increase in the overall weight of the unit, and an exponential increase in the cost. Moreover, due to the large size of the transmission chain, the difficulty and cost of transportation will also increase. Moreover, after the diameter of the single-row tapered roller bearing increases, the internal rolling element 130a becomes thicker and longer to bear a larger load, which will increase the difficulty of producing and manufacturing the rolling element 130a and the difficulty of assembling the bearing. Moreover, when the bearing is running, the excessively large rolling element 130a is prone to sliding and skewing, which accelerates the damage of the bearing.
[0031] Based on this, the embodiment of the utility model proposes a tapered roller bearing with good load-bearing capacity and small diameter. Even to adapt to high-power units, the diameter will not increase or will increase only slightly, and the size of the rolling element 130 will not increase or will increase only slightly, thereby avoiding one or more problems existing in the above-mentioned related technologies.
[0032] The following will be combined Figures 2 to 6 The invention introduces a tapered roller bearing, a shaft system structure and a wind turbine generator set provided by embodiments of the invention.
[0033] like Figure 2 , Figure 3 , Figure 4 and Figure 5 As shown, the first aspect of the utility model provides a tapered roller bearing, which includes: an inner ring 110 and an outer ring 140 that are coaxially sleeved and correspond one to one, and the inner ring 110 has a large diameter end and a small diameter end that are opposite in its own axial direction; at least two retaining frames 120, which are arranged on a raceway formed between the inner ring 110 and the outer ring 140 and distributed along the axial direction of the inner ring 110; at least two rows of rolling elements 130, at least two rows of rolling elements 130 are installed one to one on at least two retaining frames 120, each row of rolling elements 130 includes a plurality of tapered rollers distributed circumferentially, and the large diameter ends of the plurality of tapered rollers of each row of rolling elements 130 are all facing the large diameter end of the inner ring 110.
[0034] The tapered roller bearing provided in the embodiment of this aspect has a plurality of retaining frames 120 axially arranged between a pair of inner rings 110 and outer rings 140 arranged in a matching manner, and a row of rolling elements 130 is arranged in each retaining frame 120, so that the large diameter ends of the tapered rollers in at least two rows of rolling elements 130 are all facing the large diameter end of the inner ring 110. Compared with the related art in which there is only one row of rolling elements 130 between the inner ring 110 and the outer ring 140 arranged in a matching manner, and the rolling elements 130 are larger in size, the present embodiment can replace the single row of large-sized rolling elements 130 with the load being borne by at least two rows of rolling elements 130 to disperse the load, thereby configuring the bearing with smaller-sized rolling elements 130, and by increasing the number of rows of rolling elements 130, the bearing can achieve a large load-bearing capacity with the diameter unchanged or slightly changed. This not only eliminates the problems of large-sized tapered rollers that are difficult to manufacture and difficult to assemble, but also reduces the chances of tapered rollers sliding and tilting during bearing operation, ensuring that the tapered rollers are in good condition during the operation of the bearings, and keeping the bearings in good operating condition. Moreover, as the size of the tapered rollers decreases, the diameter of the tapered roller bearings can be reduced. Therefore, when tapered roller bearings are used in the main bearings of wind turbines, even if the load is large, the diameter of the tapered roller bearings is not large and will not increase too much, and the size of the transmission chain that matches it will not increase too much, which is conducive to reducing the overall cost of wind turbines, reducing the weight of the units, and facilitating transportation.
[0035] Furthermore, in some embodiments, the radial bearing capacity of at least two rows of rolling elements 130 is different. Here, the radial bearing capacity of the rolling elements 130 can be adjusted as needed. For example, the radial bearing capacity of the rolling elements 130 in the tapered roller bearing where the radial force is greater is made greater, while the radial bearing capacity of the rolling elements 130 in other places is made smaller. Under the condition of ensuring the bearing load, each row of rolling elements 130 does not have to have a larger radial bearing capacity, which is conducive to reducing the size of the tapered roller bearing.
[0036] Specifically, the radial bearing capacity of the rolling element 130 is related to its own radial size and its posture in the retaining frame 120. Of course, there may be other influencing factors, which are not listed here one by one. In this case, the radial size of this part of the rolling element 130 can be reduced so that it does not need to have a large radial bearing capacity. The small-sized rolling element 130 reduces the material consumption, is convenient for processing, and is also conducive to reducing the radial size of the tapered roller bearing. It is also possible to adjust the posture of the rolling element 130 so that it does not need to have a large radial bearing capacity, for example, by increasing the inclination angle of this part of the rolling element 130, and such a design can reduce the axial size of the tapered roller bearing. Of course, the radial size and posture of this part of the rolling element 130 can also be changed at the same time, so as to design a tapered roller bearing with small size and large bearing capacity according to actual needs.
[0037] In a specific embodiment, in any two adjacent rows of rolling elements 130, the radial bearing capacity of one row of rolling elements 130 close to the small diameter end of the inner ring 110 is smaller than the radial bearing capacity of the other row of rolling elements 130. Sharing the radial load by multiple rows of rolling elements 130 can ensure that the tapered roller bearing has sufficient radial bearing capacity, and the radial bearing capacity of the rolling elements 130 close to the small diameter end of the inner ring 110 is smaller, which can be achieved by reducing the size of the rolling elements 130 or adjusting their posture, thereby facilitating the processing of the rolling elements 130 at this location and reducing the size of the tapered roller bearing.
[0038] As an example, Figure 4 As shown, the tapered roller bearing includes two rows of rolling elements 130, with the row of rolling elements 130 on the left side of the figure near the small diameter end of the inner ring 110 being the first row of rolling elements 131, and the row of rolling elements 130 on the right side of the figure near the large diameter end of the inner ring 110 being the second row of rolling elements 132. The radial force is applied to the tapered roller bearing along the direction indicated by the arrow extending radially in the figure. The radial force borne by the first row of rolling elements 131 is smaller than the radial force borne by the second row of rolling elements 132. The radial bearing capacity of the first row of rolling elements 131 is smaller than that of the second row of rolling elements 132, so that the bearing requirements of the tapered roller bearing can be met. The radial dimension of the first row of rolling elements 131 is smaller than that of the second row of rolling elements 132. Compared with the same radial dimension of the two, it is convenient to process the first row of rolling elements 131 on the one hand, and it is helpful to reduce the diameter of the tapered roller bearing on the other hand. The raceway taper angle of the first row of rolling elements 131 is greater than the raceway taper angle of the second row of rolling elements 132. Here, a perpendicular line is drawn to the straight line in contact with the rolling element 130 and the outer ring 140. The angle between the perpendicular line and the radial line is the raceway taper angle. The raceway taper angle of the first row of rolling elements 131 is reduced, which helps to reduce the axial length of the tapered roller bearing. In this example, the radial bearing capacity of the first row of rolling elements 131 is reduced, the size of the first row of rolling elements 131 is reduced, and the size of the tapered roller bearing is reduced.
[0039] Furthermore, in some embodiments, the axial bearing capacity of at least two rows of rolling elements 130 is different. Here, the axial bearing capacity of the rolling elements 130 can be adjusted as needed. For example, the axial bearing capacity of the rolling elements 130 in the tapered roller bearing where the axial force is greater is made greater, while the axial bearing capacity of the rolling elements 130 in other places is made smaller. Under the condition of ensuring the bearing load, each row of rolling elements 130 does not have to have a larger axial bearing capacity, which is conducive to reducing the size of the tapered roller bearing.
[0040] Specifically, the axial bearing capacity of the rolling element 130 is related to its own length and its posture in the retaining frame 120. Of course, there may be other influencing factors, which are not listed here one by one. In this case, the length of this part of the rolling element 130 can be reduced so that it does not have to have a large axial bearing capacity. The small-sized rolling element 130 reduces the material consumption, is convenient for processing, and is also conducive to reducing the axial size of the tapered roller bearing. It is also possible to adjust the posture of the rolling element 130 so that it does not have to have a large axial bearing capacity, for example, by reducing the inclination angle of this part of the rolling element 130, and such a design can reduce the radial size of the tapered roller bearing, that is, the diameter. Of course, the length and posture of this part of the rolling element 130 can also be changed at the same time, so as to design a tapered roller bearing with small size and large bearing capacity according to actual needs.
[0041] In a specific embodiment, in any two adjacent rows of rolling elements 130, the axial bearing capacity of the rolling elements 130 in one row close to the small diameter end of the inner ring 110 is greater than the axial bearing capacity of the rolling elements 130 in the other row. The axial load is shared by multiple rows of rolling elements 130, which can ensure that the tapered roller bearing has sufficient axial bearing capacity, and the axial bearing capacity of the rolling elements 130 far away from the small diameter end of the inner ring 110 is smaller, which can be achieved by reducing the size of the rolling elements 130 or adjusting their posture, thereby facilitating the reduction of the size of the tapered roller bearing.
[0042] As an example, Figure 4As shown, the axial force is applied to the tapered roller bearing in the direction indicated by the arrow extending axially in the figure. The axial force borne by the first row of rolling elements 131 is greater than the axial force borne by the second row of rolling elements 132. Therefore, the axial bearing capacity of the first row of rolling elements 131 is greater than the axial bearing capacity of the second row of rolling elements 132, which can meet the bearing requirements of the tapered roller bearing. The length of the second row of rolling elements 132 is reduced relative to the first row of rolling elements 131, and compared with the equal length of the two, the axial length of the tapered roller bearing is reduced. The raceway taper angle of the second row of rolling elements 132 is smaller than the raceway taper angle of the first row of rolling elements 131. Here, a perpendicular line is drawn to the straight line in contact with the rolling element 130 and the outer ring 140. The angle between the perpendicular line and the radial line is the raceway taper angle. By reducing the raceway taper angle of the second row of rolling elements 132, the diameter of the tapered roller bearing can be reduced. Therefore, in this example, the axial bearing capacity of the second row of rolling elements 132 is reduced, the size of the second row of rolling elements 132 is reduced, and the size of the tapered roller bearing is reduced.
[0043] In some embodiments, in any two adjacent rows of rolling elements 130 , the raceway taper angle of one row of rolling elements 130 close to the small diameter end of the inner ring 110 is greater than the raceway taper angle of the other row of rolling elements 130 .
[0044] When the parameters such as the size of the rolling element 130 remain unchanged, the larger the raceway taper angle, the greater the axial bearing capacity of the rolling element 130, and the smaller the radial bearing capacity. Therefore, in any two adjacent rows of rolling elements 130, the raceway taper angle of one row of rolling elements 130 near the small diameter end of the inner ring 110 is designed to be greater than the raceway taper angle of the other row of rolling elements 130, which is conducive to making the rolling element 130 near the small diameter end of the inner ring 110 have a larger axial bearing capacity than the rolling element 130 near the large diameter end of the inner ring 110, and making the rolling element 130 near the large diameter end of the inner ring 110 have a larger radial bearing capacity than the rolling element near the small diameter end of the inner ring 110, so as to meet the large load requirements of the tapered roller bearing, and will not increase or will not increase too much the radial size of the tapered roller bearing.
[0045] Furthermore, at least two rows of rolling elements 130 include a first row of rolling elements 131 and a second row of rolling elements 132. The second row of rolling elements 132 is located on the side of the first row of rolling elements 131 close to the large diameter end of the inner ring 110. The cone angle of the raceway at the first row of rolling elements 131 ranges from 0° to 90°, and the cone angle at the second row of rolling elements 132 ranges from 0° to 45°. With the cone angle of the raceway of the first row of rolling elements 131 being greater than the cone angle of the raceway of the second row of rolling elements 132, the first row of rolling elements 131 can have a greater axial bearing capacity than the second row of rolling elements 132, and the second row of rolling elements 132 can have a greater radial bearing capacity than the first row of rolling elements 131, thereby meeting the large load requirements of the tapered roller bearing.
[0046] As an example, the raceway taper angle at the first row of rolling elements 131 ranges from 10° to 30°, and the taper angle at the second row of rolling elements 132 ranges from 10° to 30°. This is conducive to meeting the large load requirements of the tapered roller bearing, and the tapered roller bearing has a smaller diameter and a smaller axial length.
[0047] As an example, the raceway taper angle at the first row of rolling elements 131 ranges from 10° to 20°, and the taper angle at the second row of rolling elements 132 ranges from 10° to 20°. This is conducive to meeting the large load requirements of the tapered roller bearing, and the tapered roller bearing has a small diameter and the axial dimension will not increase too much.
[0048] In some embodiments, at least two rows of rolling elements 130 have different sizes. In any two adjacent rows of rolling elements 130, the axial length of one row of rolling elements 130 near the small diameter end of the inner ring 110 is greater than the axial length of the other row of rolling elements 130, and / or the diameter of the large diameter end of one row of rolling elements 130 near the large diameter end of the inner ring 110 is greater than the diameter of the large diameter end of the other row of rolling elements 130.
[0049] In addition to adjusting the axial bearing capacity and radial bearing capacity of the rolling element 130 by adjusting the raceway taper angle, this can also be achieved by adjusting the size of the rolling element 130. In these embodiments, increasing the axial length of a row of rolling elements 130 close to the small diameter end of the inner ring 110 can increase the axial bearing capacity of the row of rolling elements 130, which is conducive to meeting the large axial load requirement of the tapered roller bearing, while making the axial length of a row of rolling elements 130 relatively far away smaller, which is conducive to reducing the axial length of the tapered roller bearing. Increasing the diameter of the large diameter end of a row of rolling elements 130 close to the large diameter end of the inner ring 110 can increase the radial bearing capacity of the row of rolling elements 130, which is conducive to meeting the large radial load requirement of the tapered roller bearing, while making the diameter of the large diameter end of a row of rolling elements 130 relatively far away smaller, which is conducive to reducing the diameter of the tapered roller bearing.
[0050] As an example, Figure 4 As shown, the tapered roller bearing includes two rows of rolling elements 130, with the row of rolling elements 130 on the left side of the figure near the small diameter end of the inner ring 110 being the first row of rolling elements 131, and the row of rolling elements 130 on the right side of the figure near the large diameter end of the inner ring 110 being the second row of rolling elements 132. The axial length of the first row of rolling elements 131 is greater than the axial length of the second row of rolling elements 132, and the diameter of the large diameter end of the first row of rolling elements 131 is smaller than the diameter of the large diameter end of the second row of rolling elements 132.
[0051] Furthermore, in some embodiments, Figure 4 and Figure 5As shown, the tapered roller bearing further includes: at least one retaining ring 150, and a retaining ring 150 is provided between any two adjacent rows of rolling elements. This can prevent the rolling elements 130 from axial movement and reduce wear, so that the tapered roller bearing can maintain a good motion state for a long time.
[0052] Further, the retaining ring 150 can be detachably assembled on the inner ring 110 and / or the retaining ring 150 and the inner ring 110 are interference fit.
[0053] A single-row tapered roller bearing according to an embodiment of the present invention is described in detail below.
[0054] like Figure 4 As shown, the single-row tapered roller bearing includes an outer ring 140 , an inner ring 110 , a detachable retaining ring 150 , two cages 120 , a first row of rolling elements 131 disposed on one of the cages 120 , and a second row of rolling elements 132 disposed on the other cage 120 .
[0055] The detachable retaining ring 150 is slightly interference fitted on the inner ring 110 , and serves as a retaining edge at the large diameter end of the first row of rolling elements 131 and a retaining edge at the small diameter end of the second row of rolling elements 132 .
[0056] The raceway taper angle of the first row of rolling elements 131 is 19°, and the first row of rolling elements 131 mainly bears axial force and a small portion of radial force.
[0057] The raceway taper angle of the second row of rolling elements 132 is 13°, and the second row of rolling elements 132 mainly bears radial force and a small part of axial force.
[0058] The value of the raceway taper angle can be calculated as an optimal value according to the load of a specific project. The raceway taper angle at the first row of rolling elements 131 is greater than or equal to the raceway taper angle at the second row of rolling elements 132 .
[0059] The single-row tapered roller bearing proposed in this embodiment has an unchanged radial dimension and a slightly increased axial dimension, and the overall load-bearing capacity of the bearing is greatly improved.
[0060] Reference for assembly method of single row tapered roller bearings Figure 5 , the outer ring 140 can be placed flat on the assembly table first, and then the second row of rolling elements 132 and the corresponding retaining frame 120 are placed on the inner ring 110. The retaining ring 150 is heated to expand it and then assembled on the inner ring 110. After it cools down, it forms an interference fit with the inner ring 110. Then, the first rolling element 130 and the corresponding retaining frame 120 are assembled using the heating assembly method, and finally the outer ring 140 is assembled.
[0061] This embodiment increases the number of rows of rolling elements 130, thereby increasing the load-bearing capacity of the bearing while keeping the diameter unchanged. In addition, two rows of small-sized rolling elements 130 are used instead of a single row of large-sized rolling elements 130. The difficulty of manufacturing the rolling elements 130 and the difficulty of assembling the bearing are reduced. The rolling elements 130 are ensured to be in good posture during the operation of the bearing, and the probability of skewness and sliding is reduced, so that the bearing maintains a good operating state. In addition, in the case of the bearing diameter remaining unchanged, the size of the transmission chain of the wind turbine generator set matched therewith will not increase too much, which can reduce the weight of the entire wind turbine generator set and avoid a significant increase in cost.
[0062] Of course, in other embodiments, the number of rows of rolling elements 130 can also be three rows, or even more rows. The size of the rolling elements 130 can also be varied. For example, if the actual load axial force is large, the size of the first row of rolling elements 131 can be increased, and if the actual load radial force is large, the size of the second row of rolling elements 132 can be increased.
[0063] like Figure 6 As shown, the second embodiment of the utility model provides a shaft system structure for a wind turbine generator set, the shaft system structure includes a moving shaft 20, a fixed shaft 30 and a first bearing 40 and a second bearing 50 located between the moving shaft 20 and the fixed shaft 30, one end of the moving shaft 20 is used to connect with the hub, the first bearing 40 and the second bearing 50 are distributed at both ends of the moving shaft 20, and the bearings close to the hub in the first bearing 40 and the second bearing 50 are tapered roller bearings as described in the first embodiment above.
[0064] The shaft system structure provided in this embodiment has the tapered roller bearing provided in the first embodiment, and thus has the beneficial effects of the first embodiment, which will not be described in detail here. Moreover, the load borne by the bearing close to the hub of the shaft system structure is relatively large, so the bearing is the tapered roller bearing provided in the first embodiment, which can bear a large load without significantly increasing the bearing diameter, which is conducive to meeting the requirements of current high-power wind turbines. Figure 6 In the shaft system structure shown in the figure, the bearing on the left side of the moving shaft 20 is a tapered roller bearing provided in the embodiment of the first aspect.
[0065] Furthermore, in some embodiments, the bearing far from the hub in the first bearing 40 and the second bearing 50 is also a tapered roller bearing as in any of the above embodiments. Then the bearings at both ends of the shafting structure can bear a large load and are small in size, which is conducive to reducing the size of the transmission chain connected to the bearing.
[0066] A third aspect of the present invention provides a wind turbine generator set, comprising the shaft system structure as described in the second aspect of the present invention.
[0067] The wind turbine generator set provided by the embodiment of this aspect has the shaft system structure provided by the embodiment of the second aspect, and thus has the beneficial effects of the embodiment of the second aspect, which will not be described in detail here.
[0068] Although the embodiments of the present invention have been described in detail above, those skilled in the art may make various modifications and variations to the embodiments of the present invention without departing from the spirit and scope of the present invention. It should be understood that, in the opinion of those skilled in the art, these modifications and variations will still fall within the spirit and scope of the embodiments of the present invention as defined in the claims.
Claims
1. A tapered roller bearing, characterized in that: The tapered roller bearing comprises: An inner ring (110) and an outer ring (140) are coaxially sleeved and correspond to each other, wherein the inner ring (110) has a large diameter end and a small diameter end that are opposite to each other in its own axial direction; At least two retaining frames (120) are arranged on a raceway formed between the inner ring (110) and the outer ring and are distributed along the axial direction of the inner ring (110); At least two rows of rolling elements (130), the at least two rows of rolling elements (130) are mounted on the at least two retaining frames (120) in a one-to-one correspondence, each row of rolling elements (130) includes a plurality of tapered rollers distributed circumferentially, and the large diameter ends of the plurality of tapered rollers of each row of rolling elements (130) are all facing the large diameter end of the inner ring (110).
2. The tapered roller bearing according to claim 1, characterized in that: The radial bearing capacities of the at least two rows of rolling elements (130) are different.
3. The tapered roller bearing according to claim 2, characterized in that: In any two adjacent rows of rolling elements (130), the axial bearing capacity of one row of rolling elements (130) close to the small diameter end of the inner ring (110) is greater than the axial bearing capacity of the other row of rolling elements (130); In any two adjacent rows of rolling elements (130), the radial bearing capacity of the rolling elements (130) in one row close to the small diameter end of the inner ring (110) is smaller than the radial bearing capacity of the rolling elements (130) in the other row.
4. The tapered roller bearing according to claim 3, characterized in that: In any two adjacent rows of rolling elements (130), the rolling track taper angle of one row of rolling elements (130) close to the small diameter end of the inner ring (110) is greater than the rolling track taper angle of the other row of rolling elements (130).
5. The tapered roller bearing according to claim 4, characterized in that: The at least two rows of rolling elements (130) include a first row of rolling elements (131) and a second row of rolling elements (132). The second row of rolling elements (132) is located on one side of the first row of rolling elements (131) close to the large diameter end of the inner ring (110). The cone angle of the raceway at the first row of rolling elements (131) ranges from 0° to 90°, and the cone angle at the second row of rolling elements (132) ranges from 0° to 45°.
6. The tapered roller bearing according to claim 5, characterized in that: The cone angle of the raceway at the first row of rolling elements (131) ranges from 10° to 30°, and the cone angle at the second row of rolling elements (132) ranges from 10° to 30°.
7. The tapered roller bearing according to claim 3, characterized in that: The at least two rows of rolling elements (130) have different sizes. In any two adjacent rows of rolling elements (130), the axial length of one row of rolling elements (130) close to the small diameter end of the inner ring (110) is greater than the axial length of the other row of rolling elements (130), and / or the diameter of the large diameter end of one row of rolling elements (130) close to the large diameter end of the inner ring (110) is greater than the diameter of the large diameter end of the other row of rolling elements (130).
8. The tapered roller bearing according to any one of claims 1 to 7, characterized in that: The tapered roller bearing further comprises: At least one retaining ring (150), wherein one retaining ring (150) is disposed between any two adjacent rows of rolling bodies (130).
9. A shaft system structure for a wind turbine generator set, characterized in that: The shaft system structure comprises a moving shaft (20), a fixed shaft (30), and a first bearing (40) and a second bearing (50) located between the moving shaft (20) and the fixed shaft (30); one end of the moving shaft (20) is used for connecting with a wheel hub; the first bearing (40) and the second bearing (50) are distributed at two ends of the moving shaft (20); and the bearing of the first bearing (40) and the second bearing (50) close to the wheel hub is a tapered roller bearing according to any one of claims 1 to 8.
10. A wind turbine generator set, characterized in that: Comprising the shafting structure as claimed in claim 9.