CN113446173A - Wind generating set and transmission shaft system thereof - Google Patents

Wind generating set and transmission shaft system thereof Download PDF

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Publication number
CN113446173A
CN113446173A CN202110802827.4A CN202110802827A CN113446173A CN 113446173 A CN113446173 A CN 113446173A CN 202110802827 A CN202110802827 A CN 202110802827A CN 113446173 A CN113446173 A CN 113446173A
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CN
China
Prior art keywords
bearing
rotating shaft
wind
wind wheel
shaft system
Prior art date
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Pending
Application number
CN202110802827.4A
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Chinese (zh)
Inventor
李小伟
曹广启
孙振军
马龙
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Shanghai Electric Wind Power Group Co Ltd
Original Assignee
Shanghai Electric Wind Power Group Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Shanghai Electric Wind Power Group Co Ltd filed Critical Shanghai Electric Wind Power Group Co Ltd
Priority to CN202110802827.4A priority Critical patent/CN113446173A/en
Publication of CN113446173A publication Critical patent/CN113446173A/en
Pending legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03D—WIND MOTORS
    • F03D80/00—Details, components or accessories not provided for in groups F03D1/00 - F03D17/00
    • F03D80/70—Bearing or lubricating arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03D—WIND MOTORS
    • F03D15/00—Transmission of mechanical power
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03D—WIND MOTORS
    • F03D80/00—Details, components or accessories not provided for in groups F03D1/00 - F03D17/00
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E10/00—Energy generation through renewable energy sources
    • Y02E10/70—Wind energy
    • Y02E10/72—Wind turbines with rotation axis in wind direction

Abstract

The application provides a wind generating set and a transmission shaft system thereof, wherein the transmission shaft system comprises a static part, a rotating shaft, a first bearing and a second bearing, and the rotating shaft is used for connecting a wind wheel of the wind generating set; the first bearing is arranged between the static part and the rotating shaft at one side close to the wind wheel, and the second bearing is arranged between the static part and the rotating shaft at one side far away from the wind wheel; the static outside is located to the rotatory axle sleeve, and first bearing supports the rotation axis with the second bearing jointly, and first bearing and second bearing are single-row tapered roller bearing. The two single-row tapered roller bearings are adopted to support the rotating shaft, the single-row tapered roller bearings can bear radial and axial combined loads which are mainly radial, and have pretightening force, so that the bearing capacity of the transmission shaft system is improved, the integral rigidity of the shaft system is better, the structural deformation is smaller, the rigidity requirements of the bearings on the rotating shaft and the static part are reduced, the sizes of the rotor shaft and the static part are reduced, and the cost of the transmission shaft system is reduced.

Description

Wind generating set and transmission shaft system thereof
Technical Field
The application relates to the field of wind driven generators, in particular to a wind driven generator set and a transmission shafting thereof.
Background
At present, a transmission shaft system of a wind generating set mostly adopts a double-row spherical roller bearing, and based on the double-row spherical roller bearing, the support types of the transmission shaft system mainly comprise two types, one type is a three-point support design, and the other type is a two-point support design. The three-point support adopts a design scheme that a double-row spherical roller bearing supports a wind wheel rotating shaft and a gear box torsion arm elastic support, and the two-point support adopts a design scheme that a spherical roller bearing and a self-aligning roller bearing support the wind wheel rotating shaft or a spherical roller bearing and a cylindrical roller bearing support the wind wheel rotating shaft. The double-row spherical roller bearing has no pretightening force, and a single roller possibly has the condition of non-rotation after being loaded, so that the sliding is caused, a very large peak load is generated, and the service life of the double-row spherical roller bearing is seriously influenced; when the axial load of the wind wheel is large, the double-row spherical roller bearing is easy to have the phenomenon of single-row roller loading, so that the load of the loaded row rollers is greatly increased. For the three-point support design, all load components in the center of the wind wheel can be transmitted to the gear box, so that the difficulty and the cost of the gear box design are improved; for the design of two-point support, the integral rigidity is small, the structural deformation is large, and the requirements on the rotating shaft of the wind wheel and the bearing support structure are high. The existing supporting design of the transmission shafting can not meet the requirement of a large megawatt and heavy load wind driven generator set on economy.
Disclosure of Invention
The application provides a wind generating set and a transmission shafting thereof.
Specifically, the method is realized through the following technical scheme:
the first aspect of the embodiments of the present application provides a transmission shafting of a wind generating set, including:
a stationary member;
the rotating shaft is used for connecting a wind wheel of the wind generating set;
a first bearing provided between the stationary member and the rotating shaft on a side close to the wind wheel;
a second bearing disposed between the stationary member and the rotating shaft on a side away from the wind wheel;
the rotating shaft is sleeved on the outer side of the static part, the first bearing and the second bearing support the rotating shaft together, and the first bearing and the second bearing are single-row tapered roller bearings.
Optionally, the stationary member is a stator shaft, and the first bearing and the second bearing jointly support the rotating shaft to rotate around the stator shaft.
Optionally, the stationary member includes a first supporting member and a second supporting member, the first supporting member is sleeved on the first bearing, and the second supporting member is sleeved on the second bearing.
Optionally, the first bearing is in interference fit with the stator shaft and the rotating shaft respectively, and the second bearing is in interference fit with the stationary member and the rotating shaft respectively.
Optionally, the distance between the loaded point of the first bearing and the loaded point of the second bearing is greater than the distance between the center of the first bearing and the center of the second bearing.
Optionally, the first bearing and the second bearing respectively include an inner ring, an outer ring, a retainer arranged between the inner ring and the outer ring, and a plurality of rollers arranged in the retainer and arranged along the same circumferential direction at intervals, a radial dimension of a space formed by the plurality of rollers of the first bearing is gradually reduced from one side close to the wind wheel to one side far away from the wind wheel, and a radial dimension of a space formed by the plurality of rollers of the second bearing is gradually increased from one side close to the wind wheel to one side far away from the wind wheel.
Optionally, the load bearing capacity of the first bearing is greater than the load bearing capacity of the second bearing.
Optionally, the first bearing has a nominal contact angle greater than a nominal contact angle of the second bearing.
Optionally, the nominal contact angles of the first bearing and the second bearing are both greater than or equal to 10 ° and less than or equal to 20 °.
Optionally, the width of the first bearing is greater than the width of the second bearing; and/or the presence of a gas in the gas,
the radial dimension of the first bearing is less than the radial dimension of the second bearing.
Optionally, the axial distance of the first bearing from the second bearing is adjustable.
Optionally, the outer side wall of the rotating shaft is provided with a flange for connecting the wind wheel.
Optionally, at a position close to the first bearing, the outer side wall of the stator shaft is provided with a first limiting portion, the inner side wall of the rotating shaft is provided with a second limiting portion, one end surface of the first bearing abuts against the first limiting portion, and the other end surface of the first bearing abuts against the second limiting portion; and/or the presence of a gas in the gas,
the outer side wall of the stator shaft is provided with a third limiting part at a position close to the second bearing, the inner side wall of the rotating shaft is provided with a fourth limiting part, one end face of the second bearing is abutted against the third limiting part, and the other end face of the second bearing is abutted against the fourth limiting part.
Optionally, the stator shaft is provided with an opening near the first bearing and/or the second bearing and/or the rotating shaft is provided with an opening near the first bearing and/or the second bearing.
A second aspect of the embodiments of the present application provides a wind turbine generator system, including:
a wind wheel;
a generator comprising a stator and a rotor; and
the drive shaft system of any one of the first aspect of the embodiments of the present application, the rotor install in the rotation axis of drive shaft system is kept away from the one end of wind wheel, the stator install in the stator axle of drive shaft system is kept away from the one end of wind wheel.
According to the technical scheme provided by the embodiment of the application, the two single-row tapered roller bearings are adopted to support the rotating shaft, the single-row tapered roller bearings can bear radial and axial combined loads which mainly take the radial direction, and have pretightening force, so that the bearing capacity of the transmission shaft system is improved, the whole rigidity of the transmission shaft system is better, the structural deformation is smaller, the rigidity requirements of the bearings on the rotating shaft and a static part are reduced, the reduction of the sizes of the rotating shaft and the static part is facilitated, and the cost of the transmission shaft system is reduced.
It is to be understood that both the foregoing general description and the following detailed description are exemplary and explanatory only and are not restrictive of the application.
Drawings
The accompanying drawings, which are incorporated in and constitute a part of this specification, illustrate embodiments consistent with the present application and together with the description, serve to explain the principles of the application.
FIG. 1 is a schematic illustration of a drive line assembly according to an exemplary embodiment of the present application;
FIG. 2 is a schematic illustration of a single row tapered roller bearing shown in an exemplary embodiment of the present application;
FIG. 3 is a diagram illustrating a nominal contact angle of a single row tapered roller bearing and a force analysis of the single row tapered roller bearing according to an exemplary embodiment of the present application;
fig. 4 is a schematic diagram illustrating a positional relationship between a first bearing and a second bearing according to an exemplary embodiment of the present application.
Reference numerals:
1. a stationary member; 11. a third limiting part; 2. a rotating shaft; 21. a second limiting part; 22. a fourth limiting part; 3. a first bearing; 4. a second bearing; 5. a flange; 6. a fixed part.
Detailed Description
Reference will now be made in detail to the exemplary embodiments, examples of which are illustrated in the accompanying drawings. When the following description refers to the accompanying drawings, like numbers in different drawings represent the same or similar elements unless otherwise indicated. The embodiments described in the following exemplary embodiments do not represent all embodiments consistent with the present application. Rather, they are merely examples of apparatus and methods consistent with certain aspects of the present application, as detailed in the appended claims.
The terminology used herein is for the purpose of describing particular embodiments only and is not intended to be limiting of the application. As used in this application and the appended claims, the singular forms "a", "an", and "the" are intended to include the plural forms as well, unless the context clearly indicates otherwise. It should also be understood that the term "and/or" as used herein refers to and encompasses any and all possible combinations of one or more of the associated listed items.
It is to be understood that although the terms first, second, third, etc. may be used herein to describe various information, such information should not be limited to these terms. These terms are only used to distinguish one type of information from another. For example, first information may also be referred to as second information, and similarly, second information may also be referred to as first information, without departing from the scope of the present application. The word "if" as used herein may be interpreted as "at … …" or "when … …" or "in response to a determination", depending on the context.
The wind generating set and the transmission shaft system thereof of the present application will be described in detail below with reference to the accompanying drawings. The features of the following examples and embodiments may be combined with each other without conflict.
The wind generating set of the embodiment of the application can comprise a wind wheel, a cabin, a generator arranged in the cabin and a transmission shaft system.
FIG. 1 is a schematic diagram of a drive shaft system according to an exemplary embodiment of the present application. Referring to fig. 1, the drive shaft system of the embodiment of the present application may include a stationary member 1, a rotating shaft 2, a first bearing 3, and a second bearing 4, wherein the rotating shaft 2 is used for connecting a wind wheel. The first bearing 3 is disposed between the stationary member 1 and the rotary shaft 2 on a side close to the wind wheel, and the second bearing 4 is disposed between the stationary member 1 and the rotary shaft 2 on a side away from the wind wheel.
In this application embodiment, the static part 1 outside is located to the rotation axis 2 cover, and rotation axis 2 is supported jointly with second bearing 4 to first bearing 3, and first bearing 3 and second bearing 4 are single-row tapered roller bearing. The transmission shaft system of the embodiment of the application adopts two single-row tapered roller bearings to support the rotating shaft 2, the single-row tapered roller bearings can bear radial and axial combined loads which are mainly radial, and have pretightening force, so that the bearing capacity of the transmission shaft system is improved, the whole rigidity of the transmission shaft system is better, the structural deformation is smaller, the rigidity requirements of the bearings on the rotating shaft 2 and the static part 1 are reduced, the reduction of the sizes of the rotating shaft 2 and the static part 1 is facilitated, and the cost of the transmission shaft system is reduced.
The transmission shaft system of the embodiment of the application adopts two single-row tapered roller bearings to form two-point support.
In some embodiments, as shown in fig. 1, the stationary member 1 is a stator shaft, and the first bearing 3 and the second bearing 4 jointly support the rotating shaft 2 to rotate around the stator shaft. The first bearing 3 and the second bearing 4 support the rotation shaft 2 to rotate around the stator shaft 1, and restrict the movement of the rotation shaft 2 in other directions.
In other embodiments, the stationary member 1 includes a first supporting member and a second supporting member, wherein the first supporting member is sleeved on the first bearing 3, and the second supporting member is sleeved on the second bearing 4. In this embodiment, the first supporting member is sleeved on the inner ring of the first bearing 3, and the second supporting member is sleeved on the inner ring of the second bearing 4. It should be noted that the first bearing 3 and the second bearing 4 support the rotation of the rotation shaft 2 and restrict other movements of the rotation shaft 2.
Wherein, in some embodiments, the rotating shaft 2 is a rotating shaft of a wind wheel; in some embodiments, the rotating shaft 2 is independent of the wind wheel, which rotates to rotate the rotating shaft 2.
The generator may comprise a stator and a rotor, the stationary part 1 being rigidly connected to the stator, and the rotating shaft 2 being adapted to transmit the rotational movement of the wind wheel to the rotor.
In the embodiment of the application, the wind wheel is arranged at one end of the rotating shaft 2 and the engine room is arranged at the other end of the rotating shaft 2 along the axial direction of the transmission shaft system.
Optionally, the first bearing 3 is in interference fit with the stationary part 1 and the rotating shaft 2 respectively, and the second bearing 4 is in interference fit with the stationary part 1 and the rotating shaft 2 respectively, so that the first bearing 3 and the second bearing 4 are always in a pre-tightening state in the operation process, the overall rigidity of the transmission shaft system is improved, and the structural deformation of the transmission shaft system is relatively small under the action of a large dynamic load. It should be understood that in other embodiments, the first bearing 3 is tightly fitted with the stationary member 1 and the rotating shaft 2, and the second bearing 4 is tightly fitted with the stationary member 1 and the rotating shaft 2, respectively, so that only the overall rigidity and the structural strength of the transmission shaft system are required.
Referring to fig. 2, the first bearing 3 and the second bearing 4 respectively include an inner ring, an outer ring, a retainer disposed between the inner ring and the outer ring, and a plurality of rollers disposed on the retainer and arranged at intervals along the same circumferential direction, in this embodiment, the inner ring and the stationary member 1 are kept stationary, and the outer ring and the rotating shaft 2 are kept stationary relatively and rotate around the stationary member 1 together with the rotating shaft 2.
For the purpose that reaches first bearing 3 and static 1, rotation axis 2 interference fit respectively, second bearing 4 and static 1, rotation axis 2 interference fit respectively to the static 1 is the stator shaft as an example, can adopt following mode installation first bearing 3 and second bearing 4:
(1) separating the inner ring and the outer ring of the second bearing 4, wherein the retainer and the plurality of rollers of the second bearing 4 are not separated from the inner ring;
(2) heating the inner ring of the second bearing 4, so that the inner ring of the second bearing 4 is heated to expand, the inner ring of the second bearing 4 is sleeved on the stator shaft 1 when the inner ring of the second bearing 4 is in an expanded state, and after cooling, the inner ring of the second bearing 4 contracts and becomes small, thereby achieving the purpose of interference fit between the inner ring of the second bearing 4 and the stator shaft 1;
(3) heating the position, corresponding to the installation of the outer ring of the second bearing 4, on the rotating shaft 2 to ensure that the corresponding position of the rotating shaft 2 is heated to expand, installing the outer ring of the second bearing 4 to the corresponding position of the rotating shaft 2 at the moment, and after cooling, contracting and reducing the corresponding position of the rotating shaft 2 to achieve the purpose of interference fit between the outer ring of the second bearing 4 and the rotating shaft 2;
(4) mounting the outer ring of the first bearing 3 to the corresponding position of the rotating shaft 2 by following the heating method;
(5) sleeving the rotating shaft 2 on the stator shaft 1, so that the outer ring of the second bearing 4 is sleeved on a plurality of rollers of the second bearing 4;
(6) following the above heating method, the inner ring and the rollers of the first bearing 3 are sleeved on the stator shaft 1, so that the outer ring of the first bearing 3 is sleeved on the rollers of the first bearing 3.
Further optionally, the distance between the loaded point of the first bearing 3 and the loaded point of the second bearing 4 is greater than the distance between the center of the first bearing 3 and the center of the second bearing 4. That is, the load arm of the first bearing 3 and the second bearing 4 becomes long, and the radial load and the axial load of the first bearing 3 and the second bearing 4 at the respective load points become small, so that the first bearing 3 and the second bearing 4 can be reduced in size, and the component cost can be reduced.
Optionally, the radial size of the space formed by the plurality of rollers of the first bearing 3 gradually decreases from the side close to the wind wheel to the side far from the wind wheel, and the radial size of the space formed by the plurality of rollers of the second bearing 4 gradually increases from the side close to the wind wheel to the side far from the wind wheel, that is, the first bearing 3 and the second bearing 4 adopt a "back-to-back" arrangement mode, so that the distance between the load point of the first bearing 3 and the load point of the second bearing 4 is greater than the distance between the center of the first bearing 3 and the center of the second bearing 4.
Referring to fig. 3, when the single-row tapered roller bearing is stressed, the circle in fig. 3 is a loading point of the single-row tapered roller bearing. Referring further to fig. 4, in fig. 4, the first bearing 3 and the second bearing 4 are arranged in a back-to-back manner, the center of the first bearing 3 is 31, the load point is 32, the center of the second bearing 4 is 41, the load point is 42, and the distance between the load point of the first bearing 3 and the load point of the second bearing 4 is L1The distance between the center of the first bearing 3 and the center of the second bearing 4 is L2，L1>L2。
It should be noted that, the distance between the load point of the first bearing 3 and the load point of the second bearing 4 may be larger than the distance between the center of the first bearing 3 and the center of the second bearing 4 by using other structural layout manners, and the first bearing 3 and the second bearing 4 are not limited to the layout manner of the "back-to-back" layout manner.
The bearing capacity of the first bearing 3 is larger than that of the second bearing 4, so that the design enables one end, close to the wind wheel, of the transmission shaft system to bear larger load, and the actual stress requirement is met. In this embodiment, the bearing capacity includes an axial bearing capacity and a radial bearing capacity, the radial bearing capacity of the first bearing 3 is greater than the radial bearing capacity of the second bearing 4, and the axial bearing capacity of the first bearing 3 is greater than the axial bearing capacity of the second bearing 4.
Wherein, the bearing capacity represents the magnitude of the force (including the radial bearing force and the axial bearing force) that can be borne, as shown in fig. 3, when the single-row tapered roller bearing is stressed, the radial bearing force is FrAxial bearing force of Fa(taking into account external axial loads and derived axial forces).
The bearing capacity of the first bearing 3 is determined by parameters such as a nominal contact angle, a width and a radial dimension of the first bearing 3, and the bearing capacity of the second bearing 4 is determined by parameters such as a nominal contact angle, a width and a radial dimension of the second bearing 4, so that the bearing capacity of the first bearing 3 and/or the bearing capacity of the second bearing 4 can be designed by designing at least one of the nominal contact angle, the width and the radial dimension of the first bearing 3 and the second bearing 4, so that the bearing capacity of the first bearing 3 is larger than the bearing capacity of the second bearing 4.
In order to make the load carrying capacity of the first bearing 3 larger than the load carrying capacity of the second bearing 4, optionally the nominal contact angle of the first bearing 3 is larger than the nominal contact angle of the second bearing 4, and/or the width of the first bearing 3 is larger than the width of the second bearing 4, and/or the radial dimension of the first bearing 3 is smaller than the radial dimension of the second bearing 4. It should be noted that the width refers to a width parallel to the axial direction of the transmission shaft system, and the radial dimension includes an inner ring diameter and an outer ring diameter.
As shown in fig. 3, the nominal contact angle of the single row tapered roller bearing is α.
Alternatively, the first and second bearings 3, 4 each have a nominal contact angle greater than or equal to 10 ° and less than or equal to 20 °, illustratively, the first bearing 3 has a nominal contact angle of 15 ° and the second bearing 4 has a nominal contact angle of 10 °; for another example, the nominal contact angle of the first bearing 3 is 20 °, and the nominal contact angle of the second bearing 4 is 15 °, so as to ensure that the bearing capacity of the first bearing 3 is higher than that of the second bearing 4 on the premise of meeting the assembly requirement. According to the embodiment, the design is carried out through the sizes of the nominal contact angles of the first bearing 3 and the second bearing 4 according to the load level of the wind generating set, the optimization of the radial bearing capacity and the axial bearing capacity of the first bearing 3 and the second bearing 4 is sought, the bearing capacity of the first bearing 3 and the second bearing 4 is deeply excavated, the sizes of the first bearing 3 and the second bearing 4 are reduced, and the cost of the first bearing 3 and the cost of the second bearing 4 are reduced.
Optionally, the axial distance between the first bearing 3 and the second bearing 4 is adjustable, the axial distance between the first bearing 3 and the second bearing 4 can be adjusted by adjusting the installation position of the first bearing 3 and/or the installation position of the second bearing 4, the optimal bearing capacity, the optimal outer dimension and the optimal cost of the transmission shaft system are sought, and the requirements on large capacity, heavy load and cost control are met.
Referring again to fig. 1, the outer side wall of the rotating shaft 2 is provided with a flange 5, and the flange 5 is used for connecting a wind wheel. Can set up the flange 5 of installation wind wheel more near cabin side, the moment of flexure that wind wheel gravity produced is littleer, shortens the wheel hub of wind wheel and the distance in cabin, can be under the unchangeable condition of wind wheel center and wind wheel quality, reduces the gravity moment effect of wind wheel to the cabin, reduces first bearing 3 and second bearing 4 because of the tired alternating load of gravity production, and then reduces first bearing 3 and second bearing 4 size, reduces wind generating set cost. Alternatively, the flange 5 is rigidly connected to the rotor and the rotor, and the rotating shaft 2 can transmit the rotational movement of the rotor to the rotor.
Next, the structure of the drive shaft system will be described by taking the stationary member 1 as a stator shaft as an example.
In some embodiments, referring to fig. 1 again, at a position close to the first bearing 3, the outer side wall of the stator shaft 1 is provided with a first limiting portion, the inner side wall of the rotating shaft 2 is provided with a second limiting portion 21, one end surface of the first bearing 3 abuts against the first limiting portion, and the other end surface abuts against the second limiting portion 21. The first limiting part and the second limiting part 21 are designed to ensure that the first bearing 3 does not have displacement in the axial direction and has better axial positioning performance. Meanwhile, the first limiting part is integrally formed on the stator shaft 1, the second limiting part 21 is integrally formed on the rotating shaft 2, an independent axial positioning structure is avoided, and the structural design cost of the transmission shaft system is reduced.
In some embodiments, referring to fig. 1 again, at a position close to the second bearing 4, the outer side wall of the stator shaft 1 is provided with a third limiting portion 11, the inner side wall of the rotating shaft 2 is provided with a fourth limiting portion 22, and one end surface of the second bearing 4 abuts against the third limiting portion 11, and the other end surface abuts against the fourth limiting portion 22. The third limiting part 11 and the fourth limiting part 22 ensure that the second bearing 4 has no displacement in the axial direction and has better axial positioning performance. Meanwhile, the third limiting part 11 is integrally formed on the stator shaft 1, and the fourth limiting part 22 is integrally formed on the rotating shaft 2, so that an independent axial positioning structure is avoided, and the structural design cost of the transmission shaft system is reduced.
In the embodiment shown in fig. 1, a first position-limiting portion is disposed on an outer side wall of the stator shaft 1 at a position close to the first bearing 3, a second position-limiting portion 21 is disposed on an inner side wall of the rotating shaft 2, an end surface of one end of the first bearing 3 abuts against the first position-limiting portion, and an end surface of the other end abuts against the second position-limiting portion 21. In addition, a third limiting portion 11 is disposed on the outer side wall of the stator shaft 1, a fourth limiting portion 22 is disposed on the inner side wall of the rotating shaft 2, and one end surface of the second bearing 4 abuts against the third limiting portion 11 and the other end surface abuts against the fourth limiting portion 22.
The first, second, third and fourth limiting portions 21, 11 and 22 may be protrusions or other limiting structures.
In addition, in order to enhance the heat dissipation of the first bearing 3 and/or the second bearing 4, and also to facilitate the observation of the first bearing 3 and/or the second bearing 4 during operation, the position of the stator shaft 1 near the first bearing 3 and/or the second bearing 4 and/or the position of the rotary shaft 2 near the first bearing 3 and/or the second bearing 4 is provided with an opening. The openings may enhance the heat dissipation of the first bearing 3 and/or the second bearing 4, and may also facilitate viewing the operating conditions of the first bearing 3 and/or the second bearing 4.
The openings may comprise openings and/or slots, for example, a small number of large holes/large slots or a large number of small holes/small slots, which allow for both heat dissipation and easy viewing of the first bearing 3 and/or the second bearing 4, as well as strength and stiffness characteristics of the stator shaft 1 and the rotary shaft 2.
Referring to fig. 1 again, the end surfaces of the stator shaft 1, the rotating shaft 2 and the first bearing 3 close to one end of the wind wheel are approximately flush, and one end of the stator shaft 1 far away from the wind wheel protrudes out of one end of the rotating shaft 2 far away from the wind wheel.
The outer side wall of the stator shaft 1 protruding out of one end of the rotating shaft 2 far away from the wind wheel is further provided with a fixing part 6, and the fixing part 6 is used for being rigidly connected with the stator. Wherein, the fixing portion 6 may be a connecting flange or other fixing structure.
The bearing device bears radial and axial combined loads mainly based on the radial direction through the two single-row tapered roller bearings, improves the bearing capacity of the transmission shaft system, reduces the overall dimension of the transmission shaft system, and reduces the cost of the transmission shaft system. In addition, the single-row tapered roller bearing has pretightening force, so that the wind generating set can be ensured to have no shafting clearance, and the axial positioning is better. Meanwhile, the pretightening force of the single-row tapered roller main bearing greatly improves the overall rigidity of the transmission shaft system, the structural deformation is small, the rigidity requirements of the first bearing 3 and the second bearing 4 on the rotating shaft 2 and the stator shaft 1 are reduced, the reduction of the sizes of the rotating shaft 2 and the stator shaft 1 is facilitated, and the cost of the wind generating set is reduced. The axial bearing capacity of the first bearing 3 and the second bearing 4 can be improved by increasing the nominal contact angle of the single-row tapered roller bearing, and the axial and radial bearing capacity of the first bearing 3 and the second bearing 4 can be better coordinated. The first bearing 3 and the second bearing 4 are arranged back to back, the load of the first bearing 3 and the load of the second bearing 4 are reduced by increasing the axial distance between the first bearing 3 and the second bearing 4, and the requirements of a large megawatt, a large impeller and a heavy load direct-driven wind generating set are met.
The embodiment of the application further provides a wind generating set, which can comprise a wind wheel, a generator and the transmission shaft system of the embodiment, wherein the rotor of the generator is arranged at one end, far away from the wind wheel, of the rotating shaft 2 of the transmission shaft system, and the stator of the generator is arranged at one end, far away from the wind wheel, of the stator shaft 1 of the transmission shaft system.
The wind power generation set of the embodiment of the application is an outer rotor type direct-drive wind power generation set, and by adopting the transmission shafting of the embodiment of the application, the problem that a shafting supporting scheme adopting a double-row spherical roller bearing cannot meet the requirement of the wind power generation set with large megawatt and heavy load on economy is solved.
The above description is only exemplary of the present application and should not be taken as limiting the present application, as any modification, equivalent replacement, or improvement made within the spirit and principle of the present application should be included in the scope of protection of the present application.

Claims (15)

1. A transmission shafting of a wind generating set is characterized by comprising:
a stationary member; the rotating shaft is used for connecting a wind wheel of the wind generating set;
a first bearing provided between the stationary member and the rotating shaft on a side close to the wind wheel;
a second bearing disposed between the stationary member and the rotating shaft on a side away from the wind wheel;
the rotating shaft is sleeved on the outer side of the static part, the first bearing and the second bearing support the rotating shaft together, and the first bearing and the second bearing are single-row tapered roller bearings.
2. The drive shafting of a wind turbine generator system according to claim 1, wherein said stationary member is a stator shaft, and said first bearing and said second bearing together support said rotating shaft for rotation about said stator shaft.
3. The transmission shaft system of claim 1, wherein the stationary member comprises a first supporting member and a second supporting member, the first supporting member is disposed on the first bearing, and the second supporting member is disposed on the second bearing.
4. The drive shafting of the wind generating set according to claim 1, wherein the first bearing is in interference fit with the stationary member and the rotating shaft, and the second bearing is in interference fit with the stationary member and the rotating shaft.
5. The drive shaft system of a wind turbine generator set according to claim 1, wherein the distance between the loaded point of the first bearing and the loaded point of the second bearing is greater than the distance between the center of the first bearing and the center of the second bearing.
6. The transmission shaft system of the wind generating set according to claim 3, wherein the first bearing and the second bearing respectively comprise an inner ring, an outer ring, a retainer arranged between the inner ring and the outer ring, and a plurality of rollers arranged on the retainer and arranged along the same circumferential direction at intervals, the radial size of a space formed by the plurality of rollers of the first bearing is gradually reduced from one side close to the wind wheel to one side far away from the wind wheel, and the radial size of a space formed by the plurality of rollers of the second bearing is gradually increased from one side close to the wind wheel to one side far away from the wind wheel.
7. The drive shaft system of a wind turbine according to claim 1, wherein the first bearing has a greater load capacity than the second bearing.
8. The drive shaft system of a wind turbine generator set of claim 7, wherein the first bearing has a nominal contact angle greater than the nominal contact angle of the second bearing.
9. The drive shaft system of a wind turbine generator set according to claim 8, wherein the first bearing and the second bearing each have a nominal contact angle greater than or equal to 10 ° and less than or equal to 20 °.
10. The drive shaft system of a wind power plant according to claim 7 or 8, wherein the width of the first bearing is larger than the width of the second bearing; and/or the presence of a gas in the gas,
the radial dimension of the first bearing is less than the radial dimension of the second bearing.
11. The drive shaft system of a wind turbine generator set of claim 1, wherein an axial distance between the first bearing and the second bearing is adjustable.
12. The drive shafting of a wind generating set according to claim 1, wherein a flange is provided on the outer side wall of the rotating shaft for connecting the wind wheel.
13. The transmission shaft system of the wind generating set according to claim 2, wherein a first position-limiting portion is disposed on an outer side wall of the stator shaft at a position close to the first bearing, a second position-limiting portion is disposed on an inner side wall of the rotating shaft, an end surface of one end of the first bearing abuts against the first position-limiting portion, and an end surface of the other end of the first bearing abuts against the second position-limiting portion; and/or the presence of a gas in the gas,
the outer side wall of the stator shaft is provided with a third limiting part at a position close to the second bearing, the inner side wall of the rotating shaft is provided with a fourth limiting part, one end face of the second bearing is abutted against the third limiting part, and the other end face of the second bearing is abutted against the fourth limiting part.
14. The drive shaft system of a wind power plant according to claim 2, characterized in that the stator shaft is provided with an opening near the first bearing and/or the second bearing and/or the rotating shaft is provided with an opening near the first bearing and/or the second bearing.
15. A wind turbine generator set, comprising:
a wind wheel;
a generator comprising a stator and a rotor; and
the drive shaft system of any one of claims 1 to 14, wherein the rotor is mounted at an end of the drive shaft system where the axis of rotation is away from the rotor, and the stator is mounted at an end of the drive shaft system where the stator axis is away from the rotor.
CN202110802827.4A 2021-07-15 2021-07-15 Wind generating set and transmission shaft system thereof Pending CN113446173A (en)

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Application Number Priority Date Filing Date Title
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Publication number Priority date Publication date Assignee Title
CN113883022A (en) * 2021-10-29 2022-01-04 新疆金风科技股份有限公司 Wind generating set shafting and wind generating set
CN113969876A (en) * 2021-10-29 2022-01-25 新疆金风科技股份有限公司 Wind generating set shafting and wind generating set
CN114439903A (en) * 2021-11-30 2022-05-06 上海电气风电集团股份有限公司 Gear box integrated device and wind generating set comprising same

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CN209012000U (en) * 2018-11-23 2019-06-21 北京金风科创风电设备有限公司 The uniaxial shafting and wind power generating set of wind power generating set
CN209011999U (en) * 2018-11-23 2019-06-21 北京金风科创风电设备有限公司 The shafting and wind power generating set of wind power generating set
CN209385288U (en) * 2018-11-23 2019-09-13 北京金风科创风电设备有限公司 The shafting and wind power generating set of wind power generating set

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CN204419878U (en) * 2014-12-23 2015-06-24 东方电气集团东方汽轮机有限公司 The spindle support structure of Large-scale Wind Turbines
CN209012000U (en) * 2018-11-23 2019-06-21 北京金风科创风电设备有限公司 The uniaxial shafting and wind power generating set of wind power generating set
CN209011999U (en) * 2018-11-23 2019-06-21 北京金风科创风电设备有限公司 The shafting and wind power generating set of wind power generating set
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Publication number Priority date Publication date Assignee Title
CN113883022A (en) * 2021-10-29 2022-01-04 新疆金风科技股份有限公司 Wind generating set shafting and wind generating set
CN113969876A (en) * 2021-10-29 2022-01-25 新疆金风科技股份有限公司 Wind generating set shafting and wind generating set
CN113883022B (en) * 2021-10-29 2023-06-16 新疆金风科技股份有限公司 Shafting of wind generating set and wind generating set
CN113969876B (en) * 2021-10-29 2023-07-04 新疆金风科技股份有限公司 Wind generating set shafting and wind generating set
CN114439903A (en) * 2021-11-30 2022-05-06 上海电气风电集团股份有限公司 Gear box integrated device and wind generating set comprising same

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