CN106460802A - Roller-bearing arrangement and a wind turbine - Google Patents
Roller-bearing arrangement and a wind turbine Download PDFInfo
- Publication number
- CN106460802A CN106460802A CN201580018149.5A CN201580018149A CN106460802A CN 106460802 A CN106460802 A CN 106460802A CN 201580018149 A CN201580018149 A CN 201580018149A CN 106460802 A CN106460802 A CN 106460802A
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- CN
- China
- Prior art keywords
- raceway
- roller bearing
- rolling element
- degree
- rotation axiss
- Prior art date
- Legal status (The legal status 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 status listed.)
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Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C19/00—Bearings with rolling contact, for exclusively rotary movement
- F16C19/50—Other types of ball or roller bearings
- F16C19/505—Other types of ball or roller bearings with the diameter of the rolling elements of one row differing from the diameter of those of another row
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C19/00—Bearings with rolling contact, for exclusively rotary movement
- F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
- F16C19/34—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load
- F16C19/38—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C19/00—Bearings with rolling contact, for exclusively rotary movement
- F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
- F16C19/34—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load
- F16C19/38—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers
- F16C19/383—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone
- F16C19/385—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone with two rows, i.e. double-row tapered roller bearings
- F16C19/386—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone with two rows, i.e. double-row tapered roller bearings in O-arrangement
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C2300/00—Application independent of particular apparatuses
- F16C2300/10—Application independent of particular apparatuses related to size
- F16C2300/14—Large applications, e.g. bearings having an inner diameter exceeding 500 mm
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C2360/00—Engines or pumps
- F16C2360/31—Wind motors
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Rolling Contact Bearings (AREA)
Abstract
The invention relates to a roller-bearing arrangement, particularly a large-diameter roller-bearing arrangement for a wind turbine, comprising an outer ring and an inner ring that can be rotated about a rotational axis, relative to said outer ring, said roller-bearing arrangement comprising a first raceway in which a plurality of first roller elements are arranged and which is designed between a first ring extension of the outer ring and a second ring extension of the inner ring, said second ring extension engaging behind the first ring extension in a radial direction relative to the rotational axis.
Description
Technical field
The present invention relates to the roller bearing device of preamble according to claim 1.
Background technology
The roller bearing device is completely known in prior art and for example with so-called large-sized roller bearing
Form is used for the armature spindle for installing wind power station.Wind power station generally includes tower and can be rotatably set on tower and fill
Hanging basket when machine rack.The one end for the armature spindle being arranged in hanging basket is connected to turning with the rotor blade by wind drive
Sub- wheel hub, and the other end is directly or indirectly attached to the electromotor for generating electricity via possible actuating device.
The problem of the wind power station is, particularly in the case of wind load change, in the region of armature spindle
The middle generation high axial force along the armature spindle and power for substantially inclining perpendicular to armature spindle, needs by for installing
The roller bearing of armature spindle is absorbing these power.
By known to 10 2,007 049 087A1 of open source literature DE by double conical roller bearing install armature spindle from
And ta-king up axial forces and radial force.
2013/113 487A1 of open source literature WO are it is further proposed that using the roller bearing with two conical roller bearings
Device is used for the armature spindle for installing wind power station, and described two conical roller bearings are spaced apart in the axial direction.At this
In the case of, in the opposite end region of stator unit or rotor unit that two bearings are arranged on wind power station and part sets
Fixed axial stop is equipped with so as to the rigidity as far as possible for realizing wind load and zero-lash support.
Above-mentioned conical roller bearing is used for ta-king up axial forces and radial force.But exist be a risk that：Due to these axles
Hold and be mainly used in absorbing big axial force, therefore the inner ring and outer rings of bearing are away from each other when tilting force becomes king-sized
Ovalization mobile and that bearer ring occurs.
The teaching for belonging to 20 2,007 018 480U1 of open source literature DE of prior art proposes to arrange tilt ball track
The extra rolling track body of form is so as to solving the problem.The solution the disadvantage is that, perpendicular to axial direction act on
Power cause the inclination of tilt ball track, thus affect the even running of bearing and cause extra axial force.
Content of the invention
It is an object of the invention to provide the roller bearing device with inner ring and outer rings, by the roller bearing device gram
Take the shortcoming of prior art.Especially, even if can also be effective in the case of the high power of rotation axiss having
Inner ring and outer rings being gradually disengaged in some sections is avoided, without due to the friction of the extra axial force of this appearance or increase.
Additionally, roller bearing device can be obtained and be had low abrasion and thus there are long-acting kinetics with high performance-price ratio.
According to the present invention, by roller bearing device, particularly it is used for the large-sized roller bearing arrangement reality of wind power station
The existing purpose, the ball bearing unit include that outer shroud and internal ring, the internal ring can be rotated around rotation axiss relative to outer shroud,
Wherein roller bearing device includes the first raceway, arranges multiple first rolling elements, it is characterised in that first in first raceway
Raceway is formed between the second ring extension of the first ring extension and internal ring of outer shroud, and wherein the second ring extension is along relatively
In the rear that the radial direction of rotation axiss is bonded on the first ring extension.
Compared to prior art, the advantage according to the roller bearing device of the present invention is：First raceway is in radially side
Formed between the two ring extensions for engaging forwards, backwards so as to passing through the utilization between the first ring extension and the second ring extension
Therebetween being rigidly connected for the first rolling element formation is acted on and avoids internal ring from being separated with outer shroud in radial directions.At this
In bright, term " being bonded on rear " particularly shows the first ring extension and the second ring extension is overlapped in radial directions, and first
Ring extension is at least partially disposed between the second ring extension and rotation axiss so that compared to prior art, by root
The significantly higher stability relative to the power acted on radial direction is achieved according to the roller bearing device of the present invention.Meanwhile,
Achieve clearance substantially less in the radial direction, therefore compared to prior art kinetics show less abrasion and
There is the longer life-span.It is evident that inner ring and outer rings are rotatable, i.e., outer shroud can also be relative to internal ring around rotation
Axis rotates.Therefore it is equipped with and higher tilting force can be absorbed simultaneously according to the wind power station of the roller bearing device of the present invention
And with increased service life.
Favorable structure and other improvement projects that the present invention is understood by the description of dependent claims and refer to the attached drawing.
Preferred embodiment according to the present invention is proposed, and the first raceway is by forming on the first ring extension
The first raceway face and on the second ring extension formed the second raceway face formed, wherein the first raceway face is back to rotation
Shaft axis and the second raceway face face rotation axiss.In this case, the first raceway face and the preferred shape of the second raceway face
Cause to arrange the first rolling element between the first raceway face and the second raceway face simultaneously into the coaxial outer surface of rotation axiss
And only absorb radial force.In this case, the rotation axiss of the first rolling element especially extend parallel to rotation axiss.First rolling
Kinetoplast is preferably formed so as to only so that outer bearing and inner bearing radial support relative to each other with cylinder.Rolled using cylinder
Kinetoplast is used for supporting radial force to guarantee can to absorb at a relatively high power and is not existed and caused due to the ovalization of inner ring and outer rings
The separate risk of inner ring and outer rings.Meanwhile, even if when these high radial power act on roller bearing device, still assuring that
The low abrasion of roller bearing device and the function of minimizing clearance and even running.First ring extension and/or the second ring extension
It is preferred that being formed so as to realizing the undercutting for engagement before and after mutually to realize installing space as compact as possible with L-shaped.
A preferred embodiment according to the present invention is proposed, and roller bearing device is included with the multiple second rollings
Second raceway of kinetoplast and the 3rd raceway with multiple 3rd rolling elements.Second raceway and the second rolling element and the 3rd raceway
Preferably formed as follows with the 3rd rolling element：Direction of the inner ring and outer rings radially and independently of axial thrust and vertically
Support each other.In this case, second and the 3rd rolling element each especially formed with the shape of frustum of a cone.Therefore with favourable
Mode, only by second and the 3rd raceway or rolling element ta-king up axial forces, and the first raceway or the first rolling element are only used for inhaling
Receive radial force.
A preferred embodiment according to the present invention is proposed, and the first raceway is along the side parallel to rotation axiss
To being arranged on second and the 3rd between raceway.Therefore in an advantageous manner, it is to avoid the first ring extension and the second ring extension
As internal ring becomes to separate relative to the relative movement of outer shroud.
A preferred embodiment according to the present invention is proposed, the rotary shaft of the second rolling element and the 3rd rolling element
Line is intersected with rotation axiss in each case, and wherein the rotation axiss of the second rolling element and the 3rd rolling element rotation axiss are relative
In the section extended parallel to rotation axiss between 60 degree and 120 degree, between preferably 80 degree and 100 degree, particularly preferably basic
Upper 90 degree of angle is intersected with each other.Therefore at a relatively high axial thrust can be absorbed in an advantageous manner.
A preferred embodiment according to the present invention is proposed, relative to the minute surface perpendicular to rotation axiss, the
Two raceways and the second rolling element are substantially formed in the way of minute surface is symmetrical relative to the 3rd raceway and the 3rd rolling element.Therefore with
Favourable mode is achieved：Inner ring and outer rings are supported each other vertically independently of the direction of axial thrust.
A preferred embodiment according to the present invention is proposed, and the second raceway is by the 3rd rolling formed on outer shroud
Road surface and the 4th raceway face formed on internal ring are formed, and are set between the 3rd raceway face and the 4th raceway face
The second rolling element, and the 6th raceway that the 3rd raceway is formed is put by the 5th raceway face formed on outer shroud and on internal ring
Surface is formed, and arranges the 3rd rolling element, the wherein the 3rd and the 5th rolling between the 5th raceway face and the 6th raceway face
Road surface and/or the 4th and the 6th raceway face relative to each other have between 60 degree and 120 degree, preferably 80 degree and 100 degree it
Between, particularly preferably substantially 90 degree of angle, and/or wherein the 3rd and the 5th raceway face and/or the 4th and the 6th raceway table
Face has 25 degree to 65 degree relative to rotation axiss, preferably 40 degree to 50 degree, particularly preferably substantially 45 degree of angle.
Preferred embodiment according to the present invention is proposed, second and the 3rd rolling element there is same size.
Full symmetric roller bearing device is realized in this way.
A substituting preferred embodiment according to the present invention is proposed, and the second rolling element is than the 3rd rolling element with more
Big size is formed.Therefore independent bearing can be made in an advantageous manner to be individually adapted to for example in the not right of wind power station
Claim expected load in the case of construction.In addition by the embodiment it is contemplated that the rotation axiss of the second rolling element and the 3rd
The rotation axiss of rolling element have different angles also relative to rotation axiss.In other words, the second rolling element is relative to rotation axiss
Gradient be different from the 3rd rolling element relative to rotation axiss gradient.
A preferred embodiment according to the present invention is proposed, and outer shroud and/or internal ring are formed with multiple parts.Cause
This especially with regard to be engaged with each other in the axial direction and in radial directions before and after engagement the first and second ring extensions,
The assembling of roller bearing device is simplified in an advantageous manner.
Another theme of the present invention is wind power station, and the wind power station includes turning with multiple rotor blades
Sub- wheel hub, wherein rotor hub are connected to armature spindle in a rotationally fixed manner, and wherein armature spindle is either directly or indirectly
It is attached to electromotor, wherein wind power station includes that, for installing the bearing arrangement of armature spindle, wherein described bearing arrangement includes
Roller bearing device according to the present invention.
By means of accompanying drawing, other of the invention are obtained by the explanation of the following preferred embodiment by means of accompanying drawing thin
Section, feature and advantage.Here, accompanying drawing only shows the exemplary of the present invention and does not limit substantive inventive concept.
Description of the drawings
Fig. 1 shows the schematic cross-section of the roller bearing device of exemplary first embodiment according to the present invention.
Fig. 2 shows the schematic cross-section of the roller bearing device of exemplary second embodiment according to the present invention.
Specific embodiment
In various figures, identical part is presented with like reference characters all the time, therefore usual in each case
Also only specify or refer to once.
In FIG, it is shown that illustrate in the section according to the roller bearing device 1 of exemplary first embodiment of the present invention
Figure.
Roller bearing device 1 includes outer shroud 2 and internal ring 3.Internal ring 3 is relative to outer shroud 2 rotatable around rotation axiss 100
Install.Roller bearing device 1 includes three bearings：Be equipped with the first rolling element 11 10 form of the first raceway less first
Bearing and the larger bearing of two substantial symmetries, the larger bearing include the second rolling for being equipped with the second rolling element 21
Road 20 and it is equipped with the 3rd raceway 30 of the 3rd rolling element 31.Second and the 3rd raceway 20,30 formed as follows：Internal ring
3 and direction of the outer shroud 2 radially and independently of axial thrust and support each other vertically.This realizes in the following way：Second
With the 3rd rolling element 21,31 relative to 100 oblique arrangement of rotation axiss.
Fourth raceway face of second raceway 20 by formation on the 3rd raceway face 22 of formation on outer shroud 2 and internal ring 3
23 form.Second rolling element 21 is arranged between the third and fourth raceway face 22,23 and its running surface is the 3rd and
Run in four raceway faces 22,23.The rotation axiss of the second rolling element 21 are angled relative to rotation axiss 100 in this case
Arrange.The rotation axiss 24 of all second rotary bodies 21 are located around on the conical outer surface of the extension of rotation axiss 100.The appearance
Angle between face and rotation axiss 100 is for about 45 degree.Second rolling element 21 is each formed in the way of slightly frustum of a cone.
Relative to minute surface or the plane of symmetry, the 3rd raceway 30 is asymmetrically formed relative to the second substantially minute surface of raceway 20, institute
State minute surface or the plane of symmetry to extend perpendicular to rotation axiss 100 and positioned at second and the 3rd centre between raceway 20,30.3rd
Raceway 30 is formed by the 6th raceway face 33 formed on the 5th raceway face 32 of formation on outer shroud 2 and internal ring 3.With second
Rolling element 21 is similar, and the 3rd rolling element 31 is arranged between the 5th and the 6th raceway face 32,33 and its running surface is
Run in five and the 6th raceway face 32,33.3rd rolling element 31 is each equally formed with the shape of slightly frustum of a cone.Second
The rotation axiss 34 of the rotation axiss 24 and the 3rd rolling element 31 of rolling element 21 are relative to along rotation axiss 100 and through rotation
The section that axis 100 extends is intersected with each other with substantially 90 degree of angle.
The first raceway 10 is formed between the second raceway 20 and the 3rd raceway 30.First raceway 10 passes through shape on outer shroud 2
Into the first raceway face 12 and on internal ring 3 formed the second raceway face 13 and formed, outer shroud 2 includes the first ring extension
15 and form the first raceway face 12 on the first ring extension 15, internal ring 3 includes the second ring extension 16 and second
The second raceway face 13 is formed on ring extension 16.First and second ring extensions 15,16 are respectively undercutting and with such as lower section
Formula is arranged：Second ring extension 16 is engaged along the radial direction 101 perpendicular to rotation axiss 100 and from rotation axiss 100
At the rear of the first ring extension 15, and the first and second ring extensions 15,16 are along the direction parallel to rotation axiss 100
It is engaged with each other.In other words, the first ring extension 15 and the second ring extension 16 are overlapped in radial direction 100, and the of outer bearing 2
One ring extension 15 is arranged between the second ring extension 16 and rotation axiss 100.Second raceway face, 13 face in this case
To rotation axiss 100, the first raceway face 12 is back to rotation axiss 100.
First rolling element 11 is set between the first and second raceway faces 12,13, and first rolling element 11 is with cylinder
Shape is formed and its running surface is run in the first and second raceway faces 12,13.First and second raceway faces 12,13 set
Put on the outer surface coaxial with rotation axiss 100.The rotation axiss 14 of the first rolling element 11 are thus all the time parallel to rotary shaft
Line 100 is arranged, and therefore the first rolling element 11 only causes the radial support each other of outer bearing 2 and inner bearing 3.First and second rings prolong
Extending portion 15,16 is engaged after radial direction 101 is gone forward so that the first ring extension 15 for being connected to outer bearing 2 is arranged on inside simultaneously
And be connected to the second ring extension 16 of inner bearing and be arranged on outside, thus all radial forces are by the 11 direct suction of the first rolling element
Receive.Even if therefore in the case where there is radial force, outer bearing 2 can also be supported directly on inner bearing 3 itself.Therefore basis
The roller bearing device 1 of the present invention can absorb high radial force and do not exist the partial division of outer bearing 2 and inner bearing 3 with
And outer bearing and/or inner bearing 2, the risk of 3 ovalizations.Especially, therefore can absorb in an efficient way and generally send out in wind-force
The tilting force that occurs in power station and excessive friction and too early bearing wear are not caused.Additionally, main bearings need not be with
More expensive mode has oversized dimensions to absorb the radial force of the raising.As the first rolling element 11 is not along rotation axiss
100 carry out axial support, rolling element 11 in terms of its girth and width can than second and the 3rd rolling element 21,31 with significantly more
Little size is formed, described second and the 3rd rolling element 21,31 be mainly used in the support on axial direction.
In order to simplify assembling, outer bearing 2 is formed by the first and second external parts 4,5 preferably in the form of two parts, its
In the 5th raceway face 32 and be provided with the first ring extension 15 of the first raceway face 13 and realize on the first external part 4, and
And the 3rd raceway face 22 realize on the second external part 5.First and second external parts 4,5 are for example screwed in one by screw 6
Rise.Inner bearing 3 is preferably equally presented as multiple parts.In the present embodiment, inner bearing 3 includes three parts：First inner part
7th, the second inner part 8 and the 3rd inner part 9.First inner part 7 includes the 4th raceway face 23 and the 3rd inner part 9 includes the 6th
Raceway face 33.On the second inner part 8, the second ring extension 16 for being provided with the second raceway face 13 is formed.First, second
It is connected to each other by another screw 6 with the 3rd inner part 7,8,9.
Rolling body device 1 includes that two potted components 40, the potted component 40 are avoided positioned at outer bearing 2 and inner bearing 3
Between, the lubricant being particularly in first, second, and third raceway 10,20,30 flows out and pollutes.
It is contemplated that above-mentioned roller bearing device 1 is in the wind power station and for installing the rotor of wind power station
Axle.In this case, armature spindle is attached to inner bearing 3, while one end of armature spindle is connected to turning with multiple rotor blades
Sub- wheel hub and the other end of armature spindle are either directly or indirectly attached to the electromotor of wind power station via actuating device.
In fig. 2, it is shown that illustrate in the section according to the roller bearing device 1 of exemplary second embodiment of the present invention
Figure.According to the roller bearing device 1 of the second embodiment substantially with 1 phase of roller bearing device according to the first embodiment
With, but in the case of the roller bearing device 1 according to the second embodiment, second and 3rd bearing first do not implement for another example
Scheme is asymmetrically formed like that, but is formed asymmetrically.
Therefore, the second rolling element 21 of second bearing is formed with more large scale than the 3rd rolling element 31 of 3rd bearing.The
Two rolling elements 21 each have the nominal diameter bigger than the 3rd rolling element 31.In the present invention, the nominal diameter of rolling element is special
Do not include rolling element therebetween along the diameter of the associated rotational axis of rolling element.Additionally, the table of the second rolling element 21
The width in face is more wider than the width of the running surface of the 3rd rolling element 31 in each case.Therefore, the second raceway 20 includes
Three and the 4th raceway face 22,23, third and fourth raceway face 22,23 is same to compare the 5th and the 6th of the 3rd raceway 30
Raceway face 32,33 is wider.
The roller bearing device 1 of the present invention is used in particular for the armature spindle (not shown) for installing wind power station.Armature spindle leads to
The electromotor of wind power station is often extended to from the rotor hub for being provided with rotor blade.In this case, rotor hub
With the form design that part is independent so that as wind-force and gravity cause the moment loading for substantially inclining on armature spindle.Cause
This second and 3rd bearing unequal loading.In order to absorb the unequal loading, in a second embodiment of the present invention, first
Now it is presented as asymmetric with second bearing, i.e. the first and second bearings have various sizes of rolling element 21,31 and difference
The running surface of width and raceway 22,23,32,33.It is also contemplated that rotation axiss 24 of the second rolling element 21 in each case
And the support angle between rotation axiss 100 is less than propping up between the rotation axiss 34 and rotation axiss 100 of the 3rd rolling element 31
Support angle degree.
When the bearing that second bearing is close rotor hub setting 3rd bearing is the bearing that close electromotor is arranged
When, compared to 3rd bearing, the tilting force in second bearing region causes higher radial load.By means of second bearing
Large-size, absorbs these the bigger power occurred in second bearing.Additionally, by the less support angle of second bearing
The increasing radial force of generation is especially discharged in the best way.The reduced size of 3rd bearing can optimize roller simultaneously
The totle drilling cost of bearing arrangement 1.
Reference numerals list
1 roller bearing device
2 outer shrouds
3 internal ring
4 first external parts
5 second external parts
6 screws
7 first inner parts
8 second inner parts
9 the 3rd inner parts
10 first raceways
11 first rolling elements
12 first raceway faces
13 second raceway faces
The rotation axiss of 14 first rolling elements
15 first ring extensions
16 second ring extensions
20 second raceways
21 second rolling elements
22 the 3rd raceway faces
23 the 4th raceway faces
The rotation axiss of 24 second rolling elements
30 the 3rd raceways
31 the 3rd rolling elements
32 the 5th raceway faces
33 the 6th raceway faces
The rotation axiss of 34 the 3rd rolling elements
40 potted components
100 rotation axiss
101 radial directions.
Claims (15)
1. roller bearing device (1), is particularly used for the large-sized roller bearing arrangement (1) of wind power station, the roller bearing
Device (1) includes that outer shroud (2) and internal ring (3), internal ring (3) can be revolved around rotation axiss (100) relative to outer shroud (2)
Turn, wherein roller bearing device (1) includes arranging multiple first rolling elements in the first raceway (10), the first raceway (10)
(11), it is characterised in that the first raceway (10) extends in the second ring of the first ring extension (15) and internal ring (3) of outer shroud (2)
Formed between portion (16), wherein the second ring extension (16) is engaged along the radial direction (101) relative to rotation axiss (100)
Rear in the first ring extension (15).
2. according to claim 1 to roller bearing device (1), wherein the first ring extension (15) is at least partially disposed on
Between second ring extension (16) and rotation axiss (100).
3. roller bearing device (1) according to any one of aforementioned claim, wherein the first raceway (10) pass through
Upper the first raceway face (12) for being formed of first ring extension (15) and the second raceway in the upper formation of the second ring extension (16)
Surface (13) and formed, wherein the first raceway face (12) back to rotation axiss (100) the second raceway face (13) in the face of rotation
Shaft axis (100).
4. according to claim 3 to roller bearing device (1), wherein the first raceway face (12) and the second raceway face
(13) outer surface that is coaxial with rotation axiss (100) and overlapping each other in radial direction (101) is formed.
5. roller bearing device (1) according to any one of aforementioned claim, the rotation of wherein the first rolling element (11)
Shaft axis (14) extend parallel to rotation axiss (100), and wherein the first rolling element (11) is formed with cylinder and caused outer
Bearing (2) and the radial support each other of inner bearing (3).
6. roller bearing device (1) according to any one of aforementioned claim, wherein roller bearing device (1) include
Second raceway (20) with multiple second rolling element (21) and the 3rd raceway (30) with multiple 3rd rolling elements (31).
7. according to claim 6 to roller bearing device (1), wherein the first raceway (10) is along parallel to rotation axiss
(100) direction is arranged on second and the 3rd between raceway (20,30).
8. roller bearing device (1) according to claim 6 or 7, wherein the second raceway (20) and the second rolling element (21)
And the 3rd raceway (30) and the 3rd rolling element (31) formed as follows：Internal ring (3) radially and outer shroud (2) are vertically
Support each other and the direction independently of axial thrust.
9. according to claim 8 to roller bearing device (1), the rotation axiss (24) of wherein the second rolling element (21) are every
Kind in the case of intersect with rotation axiss (100), wherein the rotation axiss (34) of the 3rd rolling element (31) in each case with rotation
Shaft axis (100) intersect, and the rotary shaft of the rotation axiss (24) and the 3rd rolling element (31) of wherein the second rolling element (21)
Line (34) is intersected with each other with the angle between 60 degree and 120 degree relative to the section that rotation axiss (100) are extended in parallel, preferably
With between 80 degree and 100 degree, particularly preferably intersected with each other with substantially 90 degree of angle.
10. roller bearing device (1) according to claim 8 or claim 9, wherein relative to vertical with rotation axiss (100)
Minute surface, the second raceway (20) and the second rolling element (21) are relative to the 3rd raceway (30) and the 3rd rolling element (31) substantially with mirror
The symmetrical mode in face is formed.
11. roller bearing devices (1) according to any one of claim 6 to 10, wherein second and/or the 3rd rolls
Body (21,31) is formed with the shape of frustum of a cone.
12. roller bearing devices (1) according to any one of claim 6 to 11, wherein the second raceway (20) by
Upper the 3rd raceway face (22) for being formed of outer shroud (2) and the 4th raceway face (23) formation in the upper formation of internal ring (3), described
Second rolling element (21) is set between the 3rd raceway face (22) and the 4th raceway face (23), and the 3rd raceway (30) by
Upper the 5th raceway face (32) for being formed of outer shroud (2) and the 6th raceway face (33) formation in the upper formation of internal ring (3), described
3rd rolling element (31), wherein the 3rd and the 5th raceway table are set between the 5th raceway face (32) and the 6th raceway face (33)
Face (22,32) and/or the 4th and the 6th raceway face (23,33) relative to each other have the angle between 60 degree and 120 degree, excellent
Select between 80 degree and 100 degree, particularly preferably substantially 90 degree of angle, and/or wherein the 3rd and the 5th raceway face (22,32)
And/or the 4th and the 6th raceway face (23,33) there is 25 degree to 65 degree of angle relative to rotation axiss (100), preferably 40
Spend to 50 degree, particularly preferably substantially 90 degree of angle.
13. roller bearing devices (1) according to any one of claim 6 to 12, wherein second and the 3rd rolling element
Equivalently-sized or wherein second rolling element (21) of (21,31) is formed with the size bigger than the 3rd rolling element (31).
14. roller bearing devices (1) according to any one of aforementioned claim, wherein outer shroud (2) and/or internal ring
(3) formed with multiple parts.
15. wind power stations, the wind power station include the rotor hub with multiple rotor blades, wherein rotor hub with
The fixed mode of rotation is connected to armature spindle, and wherein armature spindle is either directly or indirectly attached to electromotor, wherein wind-force
Electric station is included for installing the bearing arrangement of armature spindle, it is characterised in that the bearing arrangement includes will according to aforementioned right
Roller bearing device (1) described in any one of asking.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102014104863.6A DE102014104863B4 (en) | 2014-04-04 | 2014-04-04 | Rolling bearing assembly and wind turbine |
| DE102014104863.6 | 2014-04-04 | ||
| PCT/EP2015/056217 WO2015150158A1 (en) | 2014-04-04 | 2015-03-24 | Roller-bearing arrangement and a wind turbine |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN106460802A true CN106460802A (en) | 2017-02-22 |
| CN106460802B CN106460802B (en) | 2019-11-12 |
Family
ID=52737099
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201580018149.5A Expired - Fee Related CN106460802B (en) | 2014-04-04 | 2015-03-24 | Roller bearing device and wind turbine |
Country Status (3)
| Country | Link |
|---|---|
| CN (1) | CN106460802B (en) |
| DE (1) | DE102014104863B4 (en) |
| WO (1) | WO2015150158A1 (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110388378A (en) * | 2018-04-20 | 2019-10-29 | 斯凯孚公司 | Support the bearing of the radial deformation of roller bearing and the rotary components including the bearing |
| CN110621896A (en) * | 2017-04-07 | 2019-12-27 | 蒂森克虏伯罗特艾德有限公司 | Tapered roller bearing and wind power plant |
| CN111853053A (en) * | 2019-04-26 | 2020-10-30 | 斯凯孚公司 | Rolling bearing, in particular large-diameter rolling bearing |
Families Citing this family (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102016223574A1 (en) * | 2016-11-28 | 2018-05-30 | Minebea Mitsumi Inc. | roller bearing |
| DE102018222789A1 (en) * | 2018-12-21 | 2020-06-25 | Thyssenkrupp Ag | Rolling bearing with radial retaining ring to limit radial deformation of the rolling bearing |
| DE102019106276A1 (en) | 2019-03-12 | 2020-09-17 | Schaeffler Technologies AG & Co. KG | Rotor bearing of a wind turbine Technical area |
| CN111677752A (en) * | 2020-06-29 | 2020-09-18 | 瓦房店轴承集团国家轴承工程技术研究中心有限公司 | Double-cross mutually-perpendicular yaw bearing |
| DE102021100222A1 (en) | 2021-01-08 | 2022-07-14 | Schaeffler Technologies AG & Co. KG | Process for the production of different variants of a series of round axle bearings |
| DE102022200534A1 (en) * | 2022-01-18 | 2023-08-03 | Thyssenkrupp Ag | Load-optimized slewing bearing arrangement |
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| WO2013113487A1 (en) | 2012-02-02 | 2013-08-08 | Eolotec Gmbh | Bearing unit, in particular for a wind turbine |
| DE102013100679A1 (en) * | 2013-01-23 | 2014-07-24 | Thyssenkrupp Rothe Erde Gmbh | Cylindrical roller bearings |
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- 2014-04-04 DE DE102014104863.6A patent/DE102014104863B4/en not_active Expired - Fee Related
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2015
- 2015-03-24 WO PCT/EP2015/056217 patent/WO2015150158A1/en active Application Filing
- 2015-03-24 CN CN201580018149.5A patent/CN106460802B/en not_active Expired - Fee Related
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| CN1668846A (en) * | 2002-07-15 | 2005-09-14 | 通用电气公司 | Wind power plant and arrangement of bearings therefor |
| EP1711720A1 (en) * | 2004-02-03 | 2006-10-18 | Hansen Transmissions International Bv | Roller bearing |
| CN101331334A (en) * | 2005-12-16 | 2008-12-24 | Ntn株式会社 | Roller bearing, main shaft support structure for wind-driven generator, pad and retainer segment |
| DE102006054453A1 (en) * | 2006-11-16 | 2008-05-29 | Rothe Erde Gmbh | Roller bearings, in particular center-free slewing bearings |
| DE102011003373A1 (en) * | 2011-01-31 | 2012-08-02 | Aktiebolaget Skf | Bearing assembly has roller bearings that are arranged between outer ring and respective inner ring, where cylindrical rollers are arranged between roller bearings |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110621896A (en) * | 2017-04-07 | 2019-12-27 | 蒂森克虏伯罗特艾德有限公司 | Tapered roller bearing and wind power plant |
| US10859120B2 (en) | 2017-04-07 | 2020-12-08 | Thyssenkrupp Rothe Erde Gmbh | Tapered roller bearing and wind turbine |
| CN110388378A (en) * | 2018-04-20 | 2019-10-29 | 斯凯孚公司 | Support the bearing of the radial deformation of roller bearing and the rotary components including the bearing |
| CN111853053A (en) * | 2019-04-26 | 2020-10-30 | 斯凯孚公司 | Rolling bearing, in particular large-diameter rolling bearing |
Also Published As
| Publication number | Publication date |
|---|---|
| CN106460802B (en) | 2019-11-12 |
| DE102014104863B4 (en) | 2018-02-22 |
| DE102014104863A1 (en) | 2015-10-08 |
| WO2015150158A1 (en) | 2015-10-08 |
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