DE102017205668A1 - Bearing for a turbocharger or an exhaust gas turbine, turbocharger or exhaust gas turbine with such storage and method for mounting a turbine shaft in a turbocharger or an exhaust gas turbine - Google Patents

Abstract

The invention relates to a bearing for a turbocharger or an exhaust gas turbine - with at least two bearing outer rings; - At least two rows of rolling elements at opposite axial ends of the bearing, wherein - at least one bearing outer ring in each case encloses at least one row of rolling elements to form an outer bearing raceway; - With at least one inner bearing raceway per row of rolling elements; - With an annular spacer in the axial direction between the two bearing outer rings; - With a turbine shaft supported by the rows of rolling elements. The storage according to the invention is characterized in that the spacer element is so interrupted or interruptible over its circumference that it can be pushed radially from the outside between the two bearing outer rings and the turbine shaft when mounted in the rows of rolling stock turbine shaft.

Description

The present invention relates to a bearing for a turbocharger or an exhaust gas turbine, further a turbocharger or an exhaust gas turbine with such storage and a method for mounting a turbine shaft in a turbocharger or an exhaust gas turbine, in particular according to the preamble of the independent claims.

The bearing of the turbine shaft in an exhaust gas turbocharger or an exhaust gas turbine, which is arranged in the exhaust stream, in particular a motor vehicle, is a neuralgic component, because due to the high speeds of the turbine shaft often more than 100,000 revolutions per minute and due to the high temperature stress caused by the high exhaust gas temperatures, the bearing unit is exposed to a considerable vibration load and thermal stress. Particularly unfavorable are the significant speed spread and the temperature variations in the bearing unit, which often require passing through resonance speeds and the compensation of widely varying thermal losses.

The variations occurring during operation require some axial play between the individual components in order to avoid jamming or distortion. If the reference point for the axial securing of the bearing is provided in the region of an axial end, over the axial length of the bearing Axialspieladditionen, which must be taken into account in the design. Large axial clearances, however, generally mean lower efficiency, because so-called blow-by losses can occur, since the axial displacements of the turbine shaft are correspondingly transmitted to the turbine wheel and optionally the compressor wheel and the gap dimensions on the paddle wheels must be kept sufficiently large to start up to avoid the paddle wheels in their housing.

There is thus a need for a bearing of a turbocharger or an exhaust gas turbine, in which particularly small axial play can be realized.

The present invention is therefore based on the object to provide a bearing for a turbocharger or an exhaust gas turbine and a turbocharger or a Abgasnutzturbine with a corresponding storage, in which particularly small axial play between the individual components can be implemented to the axial displacements of the turbine shaft during operation to reduce. Furthermore, a method for mounting a corresponding turbine shaft in a turbocharger or an exhaust gas turbine is to be specified.

The object of the invention is achieved by a storage with the features of claim 1. In the dependent claims, a turbocharger or an exhaust gas turbine with a corresponding storage are specified. Furthermore, the independent method claim specifies a method according to the invention for mounting a turbine shaft in a turbocharger or an exhaust gas turbine.

A bearing according to the invention for a turbocharger or an exhaust gas turbine has at least two bearing outer rings and at least two rows of rolling elements at opposite axial ends of the bearing. In each case at least one bearing outer ring encloses at least one row of rolling elements, forming an outer bearing raceway.

It is also provided at least one inner bearing raceway per row of rolling elements and an annular spacer in the axial direction between the two bearing outer rings.

The bearing further comprises a turbine shaft supported by the rows of rolling elements.

According to the invention, the spacing element is designed to be interrupted or interruptible over its circumference in such a way that it can be inserted radially from outside between the two outer bearing rings and over the turbine shaft when the turbine shaft is mounted in the rolling element rows.

In particular, the spacer has such a distance between its two circumferentially facing each other ends, that this distance at least approximately equal to the diameter of the turbine shaft or larger than the diameter of the turbine shaft, so that with or without elastic deformation, the spacer can be pushed over the turbine shaft in that the turbine shaft can be passed through this distance, possibly with elastic widening of the spacer element.

The storage according to the invention forms in particular a rolling bearing with so-called O-arrangement. With such an O-arrangement in a bearing, the setting is such that the lines of force flow through the bearings have a center of pressure axially outside the rows of rolling elements, at least outside the axial center thereof. For this purpose, the bearing outer rings have a projecting collar axially within the rows of rolling elements, against which the rolling elements of the Can create rows of rolling elements in the axial direction or in axial-radial direction. The turbine shaft may axially outside each of the rows of rolling elements have a corresponding collar to which the rolling elements can create correspondingly in the axial direction or axial-radial direction. Of course, it is possible to provide appropriate frets on both sides of the rolling elements in the region of the inner raceway and / or the outer raceway.

In order to provide a so-called direct bearing, according to one embodiment, the inner raceways of the rolling element rows are formed by an outer surface of the turbine shaft. Alternatively, at least one bearing inner ring is applied to the turbine shaft, in particular pressed on, which forms the inner raceways. For example, two bearing inner rings are provided, which can abut each other in the axial direction to form an inner raceway in each case.

It is favorable if the two bearing outer rings are elastically supported against each other in the axial direction by means of at least one spring element.

Particularly preferably, the two bearing outer rings are elastically supported in the axial direction by means of at least one spring element against the spacer element.

In both embodiments, the spring elements can advantageously be designed as a corrugated spring, in particular with individual discretely distributed over the circumference arranged contact surfaces, of which a first number or plurality of spacer or an intermediate element provided between the spacer and the corrugated spring and a second number or plurality of the respective Bear the bearing outer ring or one provided between the respective bearing outer ring and the wave spring intermediate element. In a direct axial support of the two bearing outer rings on the corrugated spring to each other are the corresponding contact surfaces on both bearing outer rings or corresponding intermediate intermediate elements.

The at least one corrugated spring may be closed or interrupted over its circumference.

In particular, the corrugated spring cooperates with or forms an anti-rotation element, for example in the form of a ring, as will be explained below, either to be held against rotation by the spacer itself or additionally to prevent rotation between the spacer element and the respective bearing outer ring manufacture. The anti-rotation element can also hold only the respective bearing outer ring relative to the spacer against rotation and advantageously at the same time form a system for the facing contact surfaces of the corrugated spring, in particular over the entire circumference.

It is particularly favorable if a stationary housing enclosing the spacer element and the bearing outer rings is provided, in particular the so-called turbocharger housing or the exhaust gas turbine housing, and the spacer element is held against rotation in the housing. Stationary means that the housing does not rotate. Such a rotation can be formed for example by a held in the housing and penetrating into the spacer or this penetrating screw or a corresponding pin. Other form-fitting or frictional configurations, in particular with at least one undercut, are possible. According to one embodiment, the spacer element is pressed into a bore of the housing, for example by inserting a spreading element into the hole in the housing in the interruption over the circumference of the spacer after the mounting of the spacer in order to clamp the spacer radially from the inside in the housing bore, or by the spacer is pushed upon insertion into the housing bore on a corresponding expansion element.

The spacer is advantageously fixed axially in the housing.

According to one embodiment of the invention, the spacer element is provided on its outer surface with at least one recess which reduces a contact surface between the spacer element and a housing receiving the spacer element. The recess advantageously extends in the axial direction of the spacer only over a limited portion, thus not over the entire axial length of the spacer. In principle, however, the latter would also be conceivable.

This recess, which is introduced, for example in the form of a groove extending in the axial direction of the spacer groove in the outer surface of the spacer, reduces the friction between the spacer and the housing during assembly. As a result, the mounting force is reduced, if the spacer has an excess to the housing bore. A lower assembly force is fundamentally advantageous in order to avoid assembly damage in storage can.

It is particularly favorable if now the spring elements are arranged against rotation of the spacer, especially if they are designed as a corrugated spring. This can namely be avoided that a spring element is rotated such that one of its contact surfaces comes to lie in the interruption of the spacer over the circumference and can no longer work properly. Alternatively, between the spring element and the spacer element, a disc bridging the interruption or a, in particular closed over its circumference, ring for bridging the interruption may be provided on which / which can support the contact surfaces.

In this case, the outer bearing rings are also particularly advantageously connected to the spacing element by means of an anti-twist device in order to avoid undefined twisting positions by co-rotation of the bearing outer rings. In this case, the same rotation can be used to prevent rotation of the spring elements relative to the spacer element as well as to prevent rotation of the bearing outer rings relative to the spacer element. Such an anti-rotation can be achieved for example by a ring with axially opposite projections projecting into each other, which engage in axial recesses in the spacer element and the respective bearing outer ring. According to another embodiment, the ring has at least one axial projection and is inserted into the respective bearing outer ring or spacer so that the at least one axial projection engages both in the bearing outer ring and in the spacer element and thereby the rotation between the respective bearing outer ring and the Distance element and in particular a corresponding engagement also produces the spring element. With such an axial projection, the axial projection for engagement in the respective bearing outer ring and the axial projection for engagement in the spacer element are integrated, so to speak, into a common axial projection. Alternatively, the spring element, in particular the corrugated spring, itself be designed with corresponding projections. The ring can also engage on the one hand with projections protruding in the axial direction in the recesses in the bearing outer ring and the spacer element and on the other bridge the interruption in the spacer element and provide a contact surface for the spring element.

According to an advantageous embodiment of the invention, it is possible to supply the rolling elements with oil via the axial recess in the bearing outer ring, which in turn lubricates and cools the rolling elements. The oil can pass through an oil inlet into a space between the housing and the bearing outer ring. In this space or annular gap, an oil ring is formed. From the oil ring, the oil passes through the axial recess in the interior of the bearing and thus to the rolling elements.

When executing the anti-rotation each as a ring these are advantageously designed as a punched or stamped and bent part with bent tabs, the latter to form the projections.

The projections advantageously engage with clearance in the recesses such that the bearing outer rings can move freely axially and radially and their rotation relative to the spacer element is limited only in the circumferential direction.

According to one embodiment of the invention, at least one projection on the side of the bearing outer ring is provided, while on the side of the spacer at least one projection usually but two projections are provided.

Another embodiment provides for two axially aligned projections, which engage in recesses provided on the outer ring and spacer and thus connect the two parts against rotation.

If an open corrugated spring used for the bearing preload, one of the two aligned projections can also be used as an anti-rotation device for the corrugated spring. This projection engages in this embodiment, not only in the bearing outer ring and the spacer but also in the gap of the open wave spring. The axial and radial freedom of movement allows optimum floating of the outer races in a squeezing oil film, when such is provided in the form of an oil ring enclosing the bearing outer rings. Such Quetschölfilm serves to damp the bearing vibrations and allows particularly high speeds.

According to an advantageous embodiment of the invention, an axial stop for each of the two bearing outer rings is provided to limit an elastic deflection of the spring or the elements. The axial stop can be formed, for example, by axially outwardly directed end faces of the spacer element against which axially inwardly directed end faces of the bearing outer rings abut after a certain compression travel of the respective spring element. Accordingly, the axially inwardly directed end faces of the bearing outer rings face the axially outwardly directed end faces of the spacer element. In particular, the corresponding outer bearing ring and / or the spacer element for this purpose has a the spring element and in particular the anti-rotation radially outwardly enclosing or cross projection or collar, which forms the corresponding front page.

By axially introduced between the bearing outer rings spacer element, which advantageously forms the starting point or fixed point for all axial play the storage, the individual axial play can be made particularly small on both sides of the spacer. Further, the bias of the bearing outer rings by the at least one spring element, in particular such that regardless of the direction of the axial load during operation, the bias is maintained to avoid undefined positions of the bearing outer rings in the axial direction. By advantageously provided stops the spring play and thus the axial play of the bearing outer rings can be limited. In summary, an extremely small relative movement of the turbine shaft in the housing of a turbocharger or an exhaust gas turbine is achieved by the design according to the invention, so that the gap dimensions on the blade or wheels can be made correspondingly low and thereby the power or the efficiency is increased.

The storage according to the invention is further optimized for a minimum outer diameter of the storage, with rows of storage with a relatively small diameter. On the other hand, if a large diameter is available for storage, comparatively large rolling element diameters can be used or the turbine shaft can be made comparatively strong. Both offer advantages, either in terms of low weight or in terms of strength and bearing life.

The rotation of the spacer in the housing is advantageously carried out by means of a screwed into a threaded bore of the spacer screw, which is held in a cylindrical bore in the housing. The cylindrical bore in the housing may have a comparatively larger diameter than the bore on the spacer or as an outer diameter of the screw shaft, so that before a complete tightening of the screw play in the axial direction and / or circumferential direction between the screw and the housing and thus between the Housing and the spacer is achieved. This allows alignment of the spacer within the housing with already screwed but not yet tightened screw. Only when the spacer is properly aligned in the housing, the screw is tightened, with a loosening of the screw can be prevented by constructive measures such as teeth on the underside of the screw head.

A great advantage of the above solution is that the screw, the thread in the spacer, the housing screw hole and the outer diameter of the spacer or the inner diameter of the bore need not be made very accurate and still a very accurate positioning of the individual components of the storage in the housing can be achieved can. By a correspondingly tightening the screw and in particular constructive measures against the loosening of the screw creep of the spacer can also be prevented relative to the housing, which is favorable in view of the extreme service life requirements of turbochargers or exhaust gas turbines.

A turbocharger according to the invention or an exhaust gas turbine according to the invention has a corresponding bearing and furthermore at least one turbine wheel carried by the turbine shaft and a compressor wheel, pinion and / or rotor of an electrical generator carried by the turbine shaft.

• – Anordnen der Wälzkörperreihen und der Lageraußenringe auf der Turbinenwelle oder auf wenigstens einem oder insbesondere zwei auf der Turbinenwelle aufgebrachten Lagerinnenringen;
• – Einschieben des Abstandselementes radial von außen axial zwischen die Lageraußenringe derart, dass es die Turbinenwelle über deren äußeren Umfang umgreift;
• – Einbringen der Turbinenwelle zusammen mit den Wälzkörperreihen, den Lageraußenringen und dem Abstandselement in das Gehäuse, insbesondere durch axiales Einschieben in eine Gehäusebohrung;
• – axiales Ausrichten wenigstens eines Lageraußenringes in dem Gehäuse;
• – anschließendes axiales und verdrehsicheres Fixieren des Abstandselementes in dem Gehäuse, insbesondere nachdem zuvor auch dieses nochmals im Gehäuse ausgerichtet wurde, vorteilhaft derart, dass die gewünschte elastische Vorspannung des Lageraußenringes gegenüber dem Abstandselement eingestellt wurde.

An inventive method for mounting a turbine shaft in a turbocharger or in an exhaust gas turbine has the following steps:

• Arranging the rows of rolling elements and the bearing outer rings on the turbine shaft or on at least one or in particular two bearing inner rings applied to the turbine shaft;
• - Inserting the spacer radially from the outside axially between the bearing outer rings such that it engages around the turbine shaft over its outer circumference;
• - Introducing the turbine shaft together with the Wälzkörperreihen, the bearing outer rings and the spacer element in the housing, in particular by axial insertion into a housing bore;
• - axially aligning at least one bearing outer ring in the housing;
• - Subsequently, axial and secure against rotation fixing the spacer element in the housing, in particular after previously this was again aligned in the housing, advantageously such that the desired elastic bias of the bearing outer ring was set relative to the spacer.

In one embodiment of the bearing with one or more spring elements, the at least one spring element is advantageously arranged on the turbine shaft before arranging the rolling element rows and the bearing outer rings.

When providing the interruption in the spacer bridging discs or Rings and / or in providing anti-rotation these are advantageously arranged in front of the rows of Wälzkörperrei and the Lageraußeringen on the turbine shaft. The spacer can then be inserted between the discs or rings.

According to one embodiment of the method according to the invention with a securing of the spacer element by means of a screw in the housing, the spacer element, in particular via a sliding fit to the housing at its outer diameter inserted into the housing and the bore, in particular threaded bore, aligned in the spacer so that they are for cylindrical screw hole in the housing is approximately concentric. Thereafter, the spacer element fixing screw is introduced from the outside through the screw hole in the housing and inserted into the bore in the spacer element, in particular screwed, initially without a firm tightening of the screw. From one axial side, in particular from the turbine side, now the turbine shaft in the direction of the other side, for example, the compressor side or pinion side or generator side, pushed until the bearing outer ring on this side with its axially outer face against a fixed stop, by a tool , in particular precision tool, can be made available, is slightly distorted. The only loosely screwed spacer is still slightly movable to the housing, due to the provided relatively large cylindrical housing bore with play to the screw shaft. In this now set precise axial position, the turbine shaft is held under slight tension by compression of the spring element between the bearing outer ring and spacer element and then the spacer fixing screw tightened. In order to prevent twisting of the spacer relative to the housing bore during tightening completely, a holding tool can be additionally introduced into the continuous interruption of the spacer, which fixes the spacer, in which it applies to the contact surfaces on the interruption side surfaces. In addition, this tool can also press the spacer against the housing bore, which ensures the anti-rotation during the tightening even safer and receives the concentricity of the spacer to the housing bore. The set axial position of the spacer is now fixed and the stop tool and the holding tool can be removed.

The invention will be described below by way of example with reference to an embodiment.

Show it:

1 a schematic exploded view of a storage according to the invention;

2 an axial section through a storage according to the invention;

3 a schematic exploded view of another storage according to the invention;

4 a schematic representation of the bearing mounted in the turbine shaft in a plan view of the interruption of the spacer element;

5 an axial section through the storage according to the 3 and 4 ,

In the 1 is a storage according to the invention, for example, for a turbocharger or a Abgasnutzturbine with a turbine wheel 1 carried by a turbine shaft 2 shown. In the embodiment shown forms the turbine shaft 2 inner raceways for a first row of rolling elements 3 and a second row of rolling elements 4 , In the illustrated embodiment, as well as from the 2 seen, the inner raceways in radially projecting portions of the turbine shaft 2 executed.

Each row of rolling elements 3 . 4 has rolling elements 5 , here in the form of bullets. The rolling elements 5 be in cages 6 held. However, this is not mandatory.

The outer raceways for the rolling elements 5 or the rows of rolling elements 3 . 4 be through bearing outer rings 7 . 8th formed, here the first bearing outer ring 7 and the second bearing outer ring 8th ,

As well as from the 2 can recognize, is in the axial direction between the two bearing outer rings 7 . 8th a spacer element 9 introduced, the interruption over its outer circumference 10 having. Since the bearings are designed as bearings with O-arrangement, see the corresponding axially within the rows of rolling elements 3 . 4 provided frets 11 at the bearing outer rings 7 . 8th , the two bearing outer rings become 7 . 8th through the spacer element 9 and spring elements 12 , which are on front sides 13 of the spacer element 9 support, elastically clamped in the axial direction. This ensures that the rolling elements 5 always with preload on the turbine shaft 2 and the bearing outer rings 7 . 8th abutment, in particular in the axial direction and radial direction, whereby noise and wear can be avoided.

To a twisting of the spring elements 12 , here executed in each case as a corrugated spring, opposite the spacer element 9 To avoid, can be a anti-rotation ring 14 each spring element 12 be provided, the at least one axial projection 15 having, in an axial recess of the spring element 12 engages, and at least one or more axial projections 16 (Only one shown in the drawing), in at least one axial recess of the spacer 9 for example, in the interruption 10 of the same, intervenes.

The axial projection 15 also engages in a corresponding axial recess 17 of the respective bearing outer ring 7 . 8th a, so that the bearing outer rings 7 . 8th opposite the spacer element 9 are secured against rotation.

If, as shown, the interruption 10 in the spacer element 9 through a disc or here the ring 14 can be bridged, on a separate axial recess in the spring element 12 into which the lead 15 engages, are also waived, for example by the axial projection 15 the corrugated spring engages around the outside or inside to radially into the axial recess 17 in the bearing outer ring 7 . 8th intervene. In such a design, it is in fact harmless, if the trained as a wave spring spring element 12 twisted, because no contact point of the same in the recess 10 can hike. By means of the axial recess 17 it is also possible the rolling elements 5 to supply them with oil which lubricates and cools them. In doing so, the oil gets over the oil inlets 27 between the case 18 and the bearing outer rings 7 . 8th brought. There then forms in the area of the bearing outer rings 7 . 8th an oil ring 25 out. About the axial recess 17 the oil gets into the storage and thus to the rolling elements 5 ,

The turbine shaft 2 becomes together with the rows of rolling elements 3 . 4 , the bearing outer rings 7 . 8th and the spacer 9 as well as the other components shown here the storage in a housing 18 introduced, for example, in an axial bore 19 thereof. The groove 28 in the radially outer surface of the spacer element 9 facilitates the insertion and alignment of the spacer 9 in the axial bore 19 because the frictional forces are reduced by the reduced applied surface. Subsequently, after a suitable alignment of the bearing outer rings 7 . 8th and the spacer element 9 the spacer element 9 in the case 18 fixed axially and radially or against rotation, here by means of the spacer fixing screw 20 in a corresponding radial bore 21 in the case 18 and a radial bore 22 in the spacer element 9 is screwed in. For example, the radial bore 22 threaded. However, the same could be the radial bore 21 be threaded and the radial bore 22 be executed in particular thread-free. The former alternative has the advantage that the orientation of the spacer element 9 in the case 18 is relieved.

In the 2 one recognizes further that between the spacer element 9 and the bearing outer rings 7 . 8th an axial stop 23 is formed, which the spring travel of the spring elements 12 limited. This axial stop is through the end faces 13 of the spacer element 9 formed, on which front sides 24 the bearing outer rings 7 . 8th attacks.

In the 2 is also an oil ring 25 per bearing outer ring 7 . 8th between the respective bearing outer ring 7 . 8th and the housing 18 provided to achieve a damping.

Furthermore, in the 2 again marked with the reference number 26 the clearance between the shank of the spacer fixing screw 20 and the housing 18 shown, which is the alignment of the spacer 9 in the case 18 facilitated. Such a game is for example between 0.1 and 0.8 mm, preferably between 0.2 and 0.5 mm.

Incidentally, in the 2 the the 1 corresponding components with the corresponding reference numerals.

In the 3 a further preferred embodiment of the invention is shown, again in a three-dimensional exploded view. The 4 shows this embodiment in a plan view and the 5 shows an axial section corresponding to the representation of the first embodiment in the 2 , only without housing. The corresponding components are again identified with the corresponding reference numerals as in the first embodiment.

Compared to the design in the 1 and 2 is in the embodiment according to the 3 to 5 the order of the arrangement of the spring element 12 and the anti-rotation ring 14 between the first bearing outer ring 7 and the spacer 9 and between the second bearing outer ring 8th and the spacer 9 reversed. However, this is not mandatory, but could also be provided an order of arrangement according to the first embodiment.

The second illustrated embodiment further differs from the first embodiment in that the two axial protrusions 15 . 16 integrated into a single projection, both in an axial recess of the spacer element 9 as well as in an axial recess 17 of the respective bearing outer ring 7 . 8th intervenes.

Notwithstanding the illustrated embodiment, in which the integrated axial projection 15 . 16 starting from the annular base body of the anti-rotation ring 14 extends only in an axial direction, the two axial projections could 15 and 16 of the anti-rotation ring 14 each other over the circumference of the anti-rotation ring 14 are directly opposite or extending in opposite axial directions integral with each other, ie aligned in the axial direction. The axial projection 16 would then turn into an axial recess of the spacer 9 engage and the axial projection 15 would be in an axial recess 17 of the respective bearing outer ring 7 . 8th intervention.

Notwithstanding the first embodiment shown, the axial projections engage 16 each in an axial recess 29 . 30 of the spacer element 9 one in addition to the interruption 10 is provided. However, this is not mandatory.

Another possible, but not mandatory deviation from the first embodiment shown is that the spring element 12 is executed interrupted over its circumference, so that the respective axial projection 16 by the interruption in the spring element 12 through in the spacer element 9 can intervene. This is also the spring element 12 against rotation relative to the bearing outer ring 8th . 9 and the spacer 9 secured.

The spring element is advantageous 12 radially within the spacer 9 positioned so that the spacer element 9 the spring element 12 encloses about the outer circumference. The anti-rotation ring 14 can in particular radially within the respective bearing outer ring 7 . 8th be positioned, at least said annular body, so that only the projection 16 radially outward into the axial recess 17 of the respective bearing outer ring 7 . 8th protrudes. In the embodiment according to the 1 and 2 however, it was advantageously provided that both the spring element 12 as well as the anti-rotation ring 14 radially within the respective bearing outer ring 7 . 8th is positioned.

Another difference in the embodiment according to the 3 to 5 is in the fact that the groove 28 on the outer surface of the spacer 9 is made substantially narrower in the axial direction. Such a groove 28 can for axial securing of the spacer element 9 serve in the housing, namely, if there is a corresponding clamping element of the housing (in the 3 to 5 not shown) is introduced.

Regarding further possible details is on in the 1 and 2 shown embodiment.

LIST OF REFERENCE NUMBERS

1

 turbine

2

 turbine shaft

3

 first row of rolling elements

4

 second row of rolling elements

5

 rolling elements

6

 Cage

7

 first bearing outer ring

8th

 second bearing outer ring

9

 spacer

10

 interruption

11

 Federation

12

 spring element

13

 front

14

 Lock Ring

15

 axial projection

16

 axial projection

17

 axial recess

18

 casing

19

 axial bore

20

 Spacer fastening screw

21

 radial bore

22

 radial bore

23

 axial stop

24

 front

25

 oil ring

26

 game

27

 oil inlet

28

 groove

29

 axial recess

30

 axial recess

Claims (20)

Storage for a turbocharger or an exhaust gas turbine 1.1 with at least two bearing outer rings ( 7 . 8th ); 1.2 with at least two rows of rolling elements ( 3 . 4 ) at opposite axial ends of the bearing, wherein each 1.3 at least one bearing outer ring ( 7 . 8th ) at least one row of rolling elements ( 3 . 4 ) encloses to form an outer bearing raceway; 1.4 with at least one inner bearing raceway per row of rolling elements ( 3 . 4 ); 1.5 with an annular spacer ( 9 ) in the axial direction between the two bearing outer rings ( 7 . 8th ); 1.6 with a through the Wälzkörperreihen ( 3 . 4 ) stored turbine shaft ( 2 ); characterized in that 1.7 the spacer element ( 9 ) is interrupted or interruptible over its circumference in such a way that it is in the Wälzkörperreihen ( 3 . 4 ) mounted turbine shaft ( 2 ) radially from the outside between the two Bearing outer rings ( 7 . 8th ) and over the turbine shaft ( 2 ) can be pushed. Bearing according to claim 1, characterized in that it forms an O-arrangement. Bearing according to one of claims 1 or 2, characterized in that the inner raceways by an outer surface of the turbine shaft ( 2 ) are formed. Bearing according to one of claims 1 to 3, characterized in that the two bearing outer rings ( 7 . 8th ) in the axial direction by means of at least one spring element ( 12 ) are elastically supported against each other. Bearing according to one of claims 1 to 4, characterized in that the two bearing outer rings ( 7 . 8th ) in the axial direction by means of at least one spring element ( 12 ) elastically against the spacer element ( 9 ) are supported. Bearing according to claim 5, characterized in that the spring elements ( 12 ) are designed as a corrugated spring. Bearing according to one of claims 1 to 6, characterized in that the spacer element ( 9 ) and the bearing outer rings ( 7 . 8th ) enclosing stationary housing ( 18 ) is provided and the spacer element ( 9 ) against rotation and axially secured in the housing ( 18 ) is held. Bearing according to claims 6 and 7, characterized in that the spring elements ( 12 ) against rotation of the spacer ( 9 ) are arranged and / or between the spring elements ( 12 ) and the spacer element ( 9 ) one the interruption ( 10 ) in the spacer element ( 9 ) bridging disc or bridging ring ( 14 ) is provided. Bearing according to one of claims 1 to 8, characterized in that the bearing outer rings ( 7 . 8th ) by means of a respective rotation against the spacer ( 9 ) are connected. Bearing according to claims 8 and 9, characterized in that the spring elements ( 12 ) with the same anti-rotation device as the bearing outer rings ( 7 . 8th ) at the spacer element ( 9 ) are connected against rotation. Bearing according to claims 8 and 9, characterized in that the interruption ( 10 ) bridging disc or the interruption ( 10 ) bridging ring ( 14 ) at the same time the rotation of the bearing outer rings ( 7 . 8th ) trains. Bearing according to one of claims 4 to 11, characterized in that an axial stop ( 23 ) for each of the two bearing outer rings ( 7 . 8th ) is provided to an elastic deflection of the spring or the ( 12 ) to limit. Bearing according to claim 12, characterized in that the axial stop ( 23 ) by axially outwardly directed end faces ( 13 ) of the spacer element ( 9 ), which axially inwardly directed end faces ( 24 ) of the bearing outer rings ( 7 . 8th ). Bearing according to one of claims 9 to 13, characterized in that the anti-rotation at least one axial recess ( 17 ) in the respective bearing outer ring ( 7 . 8th ) and at least one in the axial recess ( 17 ) engaging axial projection ( 15 ) of the spacer element ( 9 ) or the interruption ( 10 ) bridging disk or the interruption ( 10 ) bridging ring ( 14 ), and the rows of rolling elements ( 3 . 4 ) Oil for lubrication and / or cooling via the at least one axial recess ( 17 ) is supplied. Bearing according to one of claims 9 to 13, characterized in that the anti-rotation at least one axial recess ( 17 ) in the respective bearing outer ring ( 7 . 8th ) and at least one axial recess ( 29 . 30 ) at each axial end of the spacer element ( 9 ), and a ring ( 14 ) with at least two axially opposite to each other extending or integrally connected to a common projection axial projections ( 15 . 16 ), one of which is in the axial recess ( 17 ) in the respective bearing outer ring ( 7 . 8th ) and one in the axial recess ( 29 . 30 ) in the spacer element ( 9 ) intervenes. Bearing according to one of claims 1 to 15, characterized in that the bearing outer rings ( 7 . 8th ) of an oil ring ( 25 ), in particular quenching oil film, are enclosed. Bearing according to one of claims 7 to 16, characterized in that the spacer element ( 9 ) within the housing ( 18 ) by means of a screw ( 20 ) is fixed by a radial bore ( 21 ) of the housing ( 18 ) in a radial bore ( 22 ) within the spacer element ( 9 ) intervenes. Turbocharger or exhaust gas turbine with a bearing according to one of claims 7 to 17, and further comprising one of the turbine shaft ( 2 ) supported turbine wheel ( 1 ) and one of the turbine shaft ( 2 ) carried compressor wheel, pinion and / or rotor of an electric generator. Method for mounting a turbine shaft ( 2 ) in a turbocharger or an exhaust gas turbine according to claim 18, comprising the following steps: 19.1 arranging the rows of rolling elements ( 3 . 4 ) and the bearing outer rings ( 7 . 8th ) on the turbine shaft ( 2 ) or at least one or two on the turbine shaft ( 2 ) applied bearing inner rings; 19.2 Insertion of the spacer element ( 9 ) radially from the outside axially between the bearing outer rings ( 7 . 8th ) such that it is the turbine shaft ( 2 ) encompasses over its outer circumference; 19.3 Inserting the turbine shaft ( 2 ) together with the rolling element rows ( 3 . 4 ), the bearing outer rings ( 7 . 8th ) and the spacer element ( 9 ) in the housing ( 18 ); 19.4 axial alignment of at least one bearing outer ring ( 7 . 8th ) in the housing ( 18 ); 19.5 subsequent axial and secure against rotation fixing of the spacer element ( 9 ) in the housing ( 18 ). A method according to claim 19, characterized in that prior to arranging the rows of rolling elements ( 3 . 4 ) and the bearing outer rings ( 7 . 8th ) at least one spring element ( 12 ) and / or the interruption ( 10 ) in the spacer element ( 9 ) bridging discs / bridging rings ( 14 ) on the turbine shaft ( 2 ) is arranged, wherein at the provision of the interruption ( 10 ) in the spacer element ( 9 ) bridging discs / rings ( 14 ) the spacer element ( 9 ) radially from the outside axially between the discs / rings ( 14 ) is inserted.

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