DE102006028200A1 - Angle adjustable rolling bearing - Google Patents

Abstract

The invention relates to a roller bearing in a housing (3), an outer ring (4) disposed within the housing and an inner ring (5, 5a, 5b), wherein between the outer ring (4) and the inner ring (5, 5a, 5b) Variety of rolling elements (6a, 6b) is arranged and the housing is integrally formed. The housing has an outer surface (at least sectionally spherical) facing the outer ring (4), and the outer ring (4) has an outer surface (9) which is at least partially aligned with the inner surface (8) of the housing (3).

Description

Field of the invention

The The present invention relates to a rolling bearing in a housing and in particular a shaft bearing with an angle adjustable bearing in a housing.

The Invention will be with reference to the shaft bearing of the rotor in wind turbines, it is noted, however, that the bearing can also be used in other areas.

at many applications for roller bearing high axial loads occur on the shaft to be supported. To it is known from the prior art, so-called spherical roller bearings be able to use, in addition to high radial and very high To absorb axial loads. However, because of the relatively high Axial load in each case wide rows of bearings required.

A more frequent Requirement for the camps is that these because of the existing Angular errors in the bearing points are adjustable in angle (where beside Spherical roller bearings are now also used for so-called CARB bearings come).

Besides have to these bearings are also equipped with a certain radial clearance, for example, to intercept the expansions by temperature differences to be able to or because of the sensitive kinematics always has a radial play in stock. this leads to especially in multi-row bearings in addition, that from a certain load ratio radial / axial load only one rolling body row or a rolling element series predominantly is charged. The required radial clearance also allows larger axial movements the shaft or a rotor to. This leads among other things to sliding marks in the contact points in the warehouse. Also have partially used the wide inner rings as unfavorable proved because it micro-movements in the mating joints to micro-movements and thereby come to fretting corrosion and thus premature wear can.

Besides are also known floating bearing, here spherical roller bearings narrower Series can be used. The bearing effect is thereby by axial Displacement between the outer ring and a housing bore reached. The outer ring becomes because of the relatively high friction only at higher axial forces. In addition, over time it can also lead to fretting corrosion in the passfuge.

Besides it comes with many camps by the relatively small or flat Pressure angle of the rolling element rows at the different high and partially changing axial loads to relatively large Movements between the rolling elements and the raceways. This is especially critical when standing or just very slowly rotating rotors, as these movements often lead to surface injuries and thus lead to premature bearing damage.

camp with much larger pressure angles and smaller bearing clearance can to narrow down these negative effects. The in the prior art partially used spherical roller bearings with comparable width rows are but relatively big, heavy and expensive and also the case becomes essential at this size influences and thus ensures higher costs. In the case of a floating bearing there is the additional disadvantage that a Displacement between the bearing outer ring and the housing bore must be done.

Besides are also bearings with larger pressure angles been developed, which is a very low clearance when satisfied carrying capacity has. These bearings, which also comparatively small outer dimensions have double row tapered roller bearings with specially specified Pressure angles. However, these bearings lack the required angular adjustability.

Of the The present invention is therefore based on the object, a rolling bearing to disposal to ask which one as possible play-free storage and thus a better rotor guidance allowed. In addition, a targeted pressure angle determination in the case of multi-row warehouse for every row in the fixed storage is possible be. At the same time, however, a Winkeleinstellbarkeit the camp allows be.

in the Trap of a floating bearing should have a good or improved floating function be enabled by the use of cylindrical roller bearings. This is inventively a rolling bearing achieved according to claim 1.

Advantageous, not trivial embodiments and Further developments are the subject of the dependent claims. It is, however, on it pointed out that not all the objects of the invention by the objects of all claims be achieved.

The rolling bearing according to the invention has a housing and an outer ring disposed within the housing and an inner ring arranged within the housing, wherein a plurality of rolling elements is arranged between the outer ring and the inner ring. According to the invention, the housing is formed in one piece and has an outer ring facing at least section wise spherical inner surface and the outer ring has an at least partially matched to the inner surface of the housing outer surface.

Under matched surfaces In particular, such coordinated spherical surfaces understood, whose radii of curvature are coordinated.

By the bearing of the outer ring in the case Is it possible, to provide an almost backlash bearing, which nevertheless angularly adjustable in an undivided housing or individual housing sits. In other words, the invention allows or represents a angle adjustable rolling bearing in a single housing Available.

By the possibility a play-free warehouse can the ones mentioned above Disadvantages, such as the formation of fretting corrosion or the sliding marks in the contact points are avoided. The Use of an undivided or one-piece housing brings on the one hand the advantage of lower production costs and on the other hand higher accuracy of fit, because not several bearings need to be aligned. Next to it will be also the overall stability the bearing and thus its capacity by the one-piece design of the housing elevated. In other words, it is possible that in itself not angle adjustable bearings angle error in one undivided housing can balance in which case essentially no bearing air or tension is necessary.

in the Trap of a fixed deposit can thus almost play-free bearings are operated, with axial movements opposite the rotor greatly reduced or substantially excluded in the prior art become. Static and dynamic angle errors can be in the spherical surfaces of the housing and the bearing outer ring be compensated.

in the Case of a floating bearing allows the rolling bearing of the invention, for example in Case of a single or multi-row cylindrical roller bearing, axially occurring changes in length optimally balance or allow.

Prefers becomes the bearing outer ring essentially fitted without play in the associated housing.

at a further preferred embodiment is also the outer ring formed in one piece. It is partial from the prior art known, multiple or multi-part outer rings in particular for multi-row Stock available to deliver. Due to the one-piece design of the outer ring can also in the case of a fixed bearing axial movement of the rotor can be further restricted.

at a further advantageous embodiment, the inner surface of the Housing one Coating on and in another embodiment, the outer surface of the Outer ring. By the coating of the inner surface of the housing or the housing bore or the bearing outer ring a sliding pair with very low friction is achieved and thus the angular adjustability of the outer ring relative to the casing improved. As a possibility for one Such coating is for example a phosphating the respective surface or a so-called ELGO glide coating into consideration. It will prefers only one of the two surfaces, d. H. either the inner surface of the housing or the outer surface of the Inner ring provided with a coating.

at a further advantageous embodiment, the housing has at its Inner circumference at least one recess for insertion of the outer ring. Preferably becomes the spherical one inner surface of the housing interrupted by said recess. By the execution of the housing as a one-piece housing is in contrast to the prior art, no fixed housing collar and no strong lid on the opposite side required, like so far.

The Recesses are thus used for the assembly, d. H. for the introduction of the bearing outer ring. advantageously, shows the case two mutually substantially opposite recesses for Introduce of the outer ring on. It can for example, two at 180 ° to each other opposite Make flats be provided to introduce the outer ring. there becomes during assembly of the outer ring turned by 90 degrees, to the housing bore introduced and after insertion turned into its final position.

Advantageous a fixing element is arranged in at least one recess. In the said recesses of the housing for the introduction of outer ring can so that Fixielemente be introduced to close the free space and order to reduce any axial movements of the outer ring or to a hiking of the outer ring prevent or inhibit in the circumferential direction. This can preferably via a axial adjustment / clamping by means of screws and / or springs respectively.

These fixing elements can be made of metal, plastic or other suitable materials. In addition, these fixing elements can also be used to possibly To supply lubricant or to install temperature or other measuring equipment. Thus, for example, the temperature at the bearing outer and / or inner bearing ring can be measured.

Farther can the fixing elements, e.g. when worn, easily replaced.

The respective rims for rolling element guidance can become in the inventions camps Both are located on the inner ring and the outer ring and it is also possible, to combine the two variants with each other.

at In another advantageous embodiment, the rolling elements are in arranged in several rows. So it is possible, for example, the rolling elements to be arranged in two rows. In one embodiment, it is in the Rolling elements around tapered rollers, in a further embodiment, especially for Floating bearing, the rolling elements are cylindrical rollers.

at In another advantageous embodiment, the rolling elements have different rows different pressure angles. In the case of a double-row fixed deposit with the same rows of rolling elements and pressure angles arise due to the load conditions different stresses in the rows of rolling elements. In this preferred embodiment This will be unfavorable Effect through the specifically defined different pressure angles and avoided different Wälzkörpergrößen. Thus, the rows of rolling over the overall duration more even than at the above mentioned Bearings loaded with equal pressure angles. This way will a longer one Service life for the entire camp reached (in total also for both rows of rolling elements).

Farther it is also possible to provide a conical bearing seat, possibly is provided only on one of several inner rings.

Also can through an additional clamping sleeve not only the clearance, but also the match between the bearing outer ring and the housing bore be influenced, which then a slight preload in the camp is adjustable.

to Sealing of the rolling bearing or for sealing between the housing and the shaft can multi-course labyrinth seals or touching or abrasive seals are used. The concrete used Seal depends on the lubricant used and the still acceptable leakage.

at a further preferred embodiment has the rolling bearing two inner rings for the respective rows of rolling elements on and these two inner rings may preferably have different widths exhibit. In particular, by using two inner rings at the fixed campus the mating surface be reduced and thus fretting corrosion largely avoided. Due to the different width of the inner rings, it is possible the bearing at different load levels adjust in different load directions. More accurate goes in the direction of a main load direction the housing a little further inward, around an improved axial support base to enable.

at a further preferred embodiment it is also possible the bearing outer ring with one or two flats to provide in this way the Mountability in the housing too improve.

at a further preferred embodiment are on the case Housing feet or support surfaces after pulled up and / or two in the radial direction of the housing extending ears provided to the housing to fix.

These Feet and / or Ears are preferably arranged opposite each other on the housing.

Further Advantages and embodiments emerge from the attached Drawings.

In this demonstrate:

1 an inventive rolling bearing in a first embodiment;

2 an inventive rolling bearing in a second embodiment;

3 an inventive rolling bearing in a third embodiment, in particular for floating bearing applications; and

4 an inventive rolling bearing in a fourth embodiment, in particular for non-locating applications.

1 shows in the left part of a page image and in the right part of a plan view of a rolling bearing according to the invention 1 in a first embodiment. In this case, the reference character L refers to the longitudinal direction and the reference character R refers to the radial direction of the bearing.

This rolling bearing 1 has a housing or special housing 3 on, and within this housing an outer ring 4 , Inside the outer ring 4 are two rows of rolling elements 6a . 6b vorgese hen. Accordingly, the in 1 bearings also shown two inner rings 5a . 5b on, passing through a running between these inner rings intermediate ring 12 be separated. The intermediate ring 12 also serves for the axial stabilization of the two inner rings 5a and 5b and to the game setting. The housing 3 has a spherical or spherical inner surface 8th on and the outer ring 4 has an outer surface 9 or the housing 3 facing surface 9 on that on the inside surface 8th of the housing 3 is adjusted. This means that the radii of curvature of these two surfaces substantially coincide with each other. Thus, an angular adjustability of the outer ring relative to the housing is made possible, although the actual bearing or the outer ring is not angularly adjustable with respect to the inner ring.

On this way you can also unwanted movements, For example, minimizes axial movement of the rings against each other or excluded.

It can be seen that the two rolling bearing rows and also the running surfaces of the two inner rings 5a . 5b lead to different pressure angles. These higher pressure angles are also possible because the bearing itself is not adjustable in angle, but the angular adjustment is achieved by the spherical surfaces. At the in 1 embodiment shown are as rolling elements 6a . 6b each used tapered rollers. In the 1 left row with the rolling elements 6a has a larger main pressure angle to accommodate the Axiallast cheaper. More specifically, a smaller deflection is achieved.

The arrangement of the two roller bearing rows in O arrangement, the shaft can also be better supported and the deflection can be reduced. At the in 1 shown double-row tapered roller bearings can thus be absorbed almost uniformly by a variety of radial and axial forces by selectively selected pressure angle.

In the case of the respective left partial images in the 1 - 4 It should be noted that in the respective upper section I and in the lower section II different bearing designs are shown. In 1 shows the upper portion I a innenringbordgeführtes rolling bearing, ie here are on the two inner rings 5a and 5b each outer borders 22 and inner shelves 23 for guiding the rolling elements 6a . 6b intended. The outer ring points in the in 1 shown upper part of image I the opposite no shelves.

In the in 1 Section II shown below are on the outer ring 4 outer shelves 21 and inner shelves 24 intended. The inner rings 5a . 5b However, they have no shelves here. In the right part of 1 denotes the reference numeral 13 a recess provided in the housing. Through this recess can be inserted into the housing during assembly of the outer ring, wherein it is preferably rotated in the insertion process by 90 ° relative to the housing bore. Through this recess results in a cavity 16 between the outer surface 9 of the outer ring 4 and the inner surface 8th of the housing 3 ,

In this cavity, the fixing device 15 (left part of the picture), where the in 1 shown embodiment, for example, a clamping sleeve or the like can act. This fixing device 15 is in the axial direction of the bearing or laterally by an outer ring 17 stabilized, the outer ring 17 with screw connections 17a is attached to the housing. The reference numerals 14 refer to seals, which are designed for example in the form of multi-course labyrinth seals.

The reference number 19 refers to an additional ring, which also serves as a tread for the seals 14 serves.

The reference number 18 indicates a hole in the outer ring 17 used for the axial attachment of the fixing device 15 serves. It is possible, for example, the fixing device 15 be secured in the axial direction by screws, but it can also be used in addition to or instead of the screws spring elements for axial securing.

It would also be possible in a further embodiment, instead of or in addition to the recesses 13 provide two opposing flats of the outer ring in order to insert these during assembly in the housing can. At the in 1 shown embodiment, the width b1 of the left inner ring 5a slightly higher than the width b2 of the right inner ring 5b , This is clear from the fact that the drawn center line M slightly opposite to the geometric center between the two inner rings 5a and 5b is offset. In other words, the housing extends 3 in the main load direction, ie in 1 from the left side, further inward to allow an improved axial support base. Accordingly, for example, a wind turbine or the like would be in 1 hung on the left side.

In addition, as stated above, the pressure angle of the left roller row is greater than that of the right roller row, whereby the load bearing of the radial force and especially the Hauptaxialkraft on the left side can be done cheaper. The smaller one Pressure angle of the right bearing row is suitable for load absorption of the radial force and possibly occurring in the opposite direction but lower axial force.

The reference number 10 refers to feet or ears in the radial direction R in 1 protrude up and down from the housing. These feet or ears are used to attach the housing and thus the camp. This embodiment is particularly suitable for use in wind turbines or generally for those applications where a significant axial force occurs. In this case, this axial force through the two feet or ears 10 be collected particularly low and at the same time the risk of bending the housing against the ears are avoided. In addition, between the feet or ears 10 and the housing 3 Also further (not shown) may be provided, for example, in the radial direction of the housing extending support surfaces.

2 shows a further embodiment of the in 1 shown warehouse. Unlike the in 1 embodiment shown here is the housing 3 on one foot 11 arranged or connected with it, as is usual in the prior art.

3 shows an embodiment of a cylindrical roller bearing. Again, the rolling elements 6a . 6b arranged in two rows between an inner ring 5 and an outer ring 4 , The rolling elements are designed here as cylindrical rollers and the raceways extend substantially in the axial direction L. The rolling elements 6a . 6b are in this embodiment by Borde 21 . 24 at the bearing outer ring 4 guided. This is therefore a floating bearing housing with a double-row cylindrical roller bearing, but also single or multi-row roller bearings are possible. Also at the in 3 the embodiment shown, the outer ring 4 be inserted into the housing almost without play. Also here on the surfaces 8th respectively. 9 that is, be provided on the surface in the housing bore or the lateral surface of the outer ring coatings. In addition to the in 3 In the embodiment shown, the bearing may generally be N type (no outer race rim, two inner race rims), NU (two outer race rims, no inner race rim), or other cylindrical roller bearing type.

Also at the in 3 embodiment shown is a fixing agent 15 provided to the free space due to the recess 13 close in the case. So that sits in here too 3 cylindrical roller bearing shown in two rows angle adjustable in the housing 3 , In this embodiment, a high load capacity is also given and a compensation of angular errors easily possible. By using the cylindrical roller bearing, the floating bearing function can be realized in a particularly favorable manner.

In order to can occurring changes in length be optimally balanced.

Also at the in 3 As shown in FIG 1 shown embodiment, side ears 10 provided for supporting and holding the housing 3 serve.

4 shows a further embodiment of the in 3 shown warehouse. This in 4 shown bearing differs from that in 3 shown bearings, as well as here in place of the lateral ears 10 a foot 11 is provided with the housing 3 communicates.

All in all allow the bearings of the invention both a high load capacity as well as a compensation of angular errors and in particular at fixed storage, e.g. Tapered roller bearings double row, a very tight axial guidance of the Rotor.

All Features disclosed in the application documents are considered to be essential to the invention as long as they are individually or in combination with respect to State of the art are new.

1

roller bearing

3

casing

4

outer ring

5

Inner ring ( 3 and 4 )

5a, 5b

inner rings

6a, 6b

rolling elements

8th

Inner surface of the housing 3

9

Surface of the outer ring 4

10

ears, feet

11

foot

12

intermediate ring

13

recesses

14

seals

15

fixing

16

cavity

17

outer ring

17a

fittings

18

drilling

19

additional ring

21 22, 23, 24

Borde

M

centerline

b1

Width of the inner ring 5a

b2

Width of the inner ring 5b

R

radial Direction of the camp

L

longitudinal direction of the camp

Claims (11)

Rolling bearings in a housing ( 3 ), an outer ring arranged inside the housing ( 4 ) and an inner ring ( 5 . 5a . 5b ), between the outer ring ( 4 ) and the inner ring ( 5 . 5a . 5b ) a plurality of rolling elements ( 6a . 6b ) is arranged, characterized in that the housing is integrally formed and a the outer ring ( 4 ) facing at least partially spherical inner surface ( 8th ), and the outer ring ( 4 ) at least in sections on the inner surface ( 8th ) of the housing ( 3 ) matched outer surface ( 9 ) having. Rolling bearing according to claim 1, characterized in that the outer ring ( 4 ) is formed in one piece. Rolling bearing according to at least one of the preceding claims, characterized in that the inner surface ( 8th ) of the housing has a coating. Rolling bearing according to at least one of the preceding claims, characterized in that the outer surface ( 9 ) of the outer ring ( 4 ) has a coating. Rolling bearing according to at least one of the preceding claims, characterized in that the housing ( 3 ) at its inner circumference at least one recess ( 13 ) for inserting the outer ring ( 4 ) having. Rolling bearing according to claim 5, characterized in that the housing has two mutually substantially opposite recesses ( 13 ) for inserting the outer ring ( 4 ) having. Rolling bearing according to claim 5, characterized in that in at least one recess a fixing element ( 15 ) is arranged. Rolling bearing according to at least one of the preceding claims, characterized in that the rolling bodies ( 6a . 6b ) are arranged in several rows. Rolling bearing according to at least one of the preceding claims, characterized in that the rolling bodies ( 6a . 6b ) of different rows and different pressure angles. Rolling bearing according to at least one of the preceding claims, characterized in that two inner rings ( 5a . 5b ) having different widths (b1, b2). Rolling bearing according to at least one of the preceding claims, characterized in that on the housing ( 3 ), in particular two in the radial direction (R) of the housing ( 3 ) extending feet and / or ears ( 10 ) are provided to the housing ( 3 ) to fix.