DE102010054904A1 - Bearing cartridge for a turbocharger - Google Patents

Abstract

The invention relates to a bearing cartridge for a turbocharger, comprising a carrier ring 11, 12, 33, which can be pressed into a bearing housing 15, 16, and a bearing outer ring 13, 14, 34 surrounded radially by the carrier ring 11, 12, 33, wherein between the cylindrical outer surface of the bearing outer ring 13 , 14, 34 and the hollow cylindrical inner surface of the carrier ring 11, 12, 33 an oil-filled intermediate space is formed and the carrier ring 11, 12, 33 has a supply bore 25 designed for supplying oil to the intermediate space, the supply bore 25 with a circumferential and is at least partially formed by the bearing outer ring, first groove 23 communicating. A user-friendly, transportable and factory pre-installable turbocharger bearing cartridge should be specified. This is achieved in that the bearing outer ring 13, 14, 34 has at least one rolling element raceway and the carrier ring 11, 12, 33 can be fastened in the bearing housing. The result is a high-performance, factory-assembled turbocharger bearing cartridge with a small number of components.

Description

Field of the invention

The invention relates to a bearing cartridge for a turbocharger comprising a carrier ring which can be pressed into a bearing housing and a bearing outer ring radially encompassed by the carrier ring, wherein a space filled with oil is formed between the cylindrical outer surface of the bearing outer ring and the hollow cylindrical inner surface of the carrier ring and the carrier ring has an oil supply the supply bore formed with a circumferentially circumferential and at least partially formed by the bearing outer ring, the first groove is communicatively connected.

Background of the invention

A turbocharger is usually used to increase the performance of internal combustion engines through the use of exhaust gas energy. The turbocharger consists of a compressor and a turbine, which are connected to each other via a shaft mounted within a bearing housing shaft. In operation, the turbine is rotated by an exhaust gas flow and drives the compressor via the shaft, which sucks and compresses air. The compressed air is conducted into the engine, whereby a large amount of air enters the cylinders due to the increased pressure during the intake stroke. As a result, the oxygen content required for the combustion of fuel increases accordingly, so that more oxygen enters the combustion chamber of the engine at each intake stroke.

This leads to an increase in the maximum torque, whereby the power output, ie the maximum power at a constant working volume, is increased. This increase allows in particular the use of a more powerful engine with approximately the same dimensions or alternatively allows a reduction in engine dimensions, so achieving a comparable performance in smaller and lighter machine.

During operation of a turbocharger, the shaft rotates at high engine speed as the engine speed increases. Due to the high rotational speed, for example, vibrations caused by the rotation of the shaft can be transmitted to the bearing cartridge. In order to prevent unwanted contact of the bearing cartridge with the bearing housing as possible and to ensure trouble-free operation of a turbocharger, usually storage units are used, which can dampen the vibrations occurring by a so-called Quetschölfilm. For this purpose, oil from the engine oil circuit is pressed into a space between the bearing cartridge and the bearing housing, wherein the resulting oil cushion or Quetschölfilm takes over the function of the vibration damper. As a result, any contact-related noise can be prevented and the service life of the individual bearing components can be increased.

Out DE 3617402 A1 turbocharger bearing cartridges are known which have a bearing with a multi-part outer ring and are arranged in a carrier ring. There is also a so-called squeeze film designed for vibration inhibition.

Thus turbocharger bearing cartridges are known from the prior art, which, thanks to a corresponding one, can be easily handled without exposing the interspace of the squeeze film. However, it is disadvantageous that a corresponding decoupling device is needed, which requires a large number of parts and is therefore expensive.

Object of the invention

It is therefore an object of the invention to provide a comparison with the prior art easily manageable turbocharger bearing cartridge available, which has a small number of components. but equally has the usual advantages of known turbocharger bearing cartridges.

Solution of the task

The object of the invention is achieved in a bearing cartridge of the type mentioned above in that the bearing outer ring has at least one Wälzkörperlaufbahn and the support ring in the bearing housing can be fastened.

The bearing outer ring is radially encompassed by the support ring, wherein between the cylindrical outer surface of the bearing outer ring and the inner surface of the support ring, a space filled with vibration-inhibiting oil space is formed. This is the so-called squeeze film, which should have uniform thickness at all points during operation as well. The support ring has a supply bore formed for supplying oil to the intermediate space, wherein the supply bore communicates with a circumferential first circumferential groove and formed at least partially by the bearing outer ring. He leads oil from the bearing housing further radially inward to the camp.

In an advantageous embodiment, the bearing cartridge can be secured in the bearing housing by means of a radial clearance fit or a radial transition fit. A clearance would be made by an appropriate choice of Outer diameter of the carrier ring to be implemented. In a negative clearance, the outer diameter of the carrier ring is slightly larger than the inner diameter of the bearing housing. Therefore, a press-fitting of the bearing cartridge would indeed necessary, but would also make additional security devices, such as an axial fixation or clamping or attachment of the carrier ring via a mounting flange provided on the mounting flange superfluous. However, if a positive radial play between the carrier ring and the bearing housing be asked, such an axial attachment method would be useful. The carrier ring could have bores in the axial direction, which allow a screw connection of the carrier ring with the housing. Alternatively, an axial stop on a hollow cylindrical constriction of the bearing housing receptacle in combination with an axial fastening element could also be used for axial attachment. However, in a positive game to pay attention to the vibration characteristics of the housing-bearing assembly.

Furthermore, there is the possibility of a radial transition fit. Here, the inner diameter of the bearing housing and the outer diameter of the carrier ring are the same size except for manufacturing tolerances. This results in a press fit with a relatively low adhesion, which realizes an attachment of the carrier ring in the bearing housing. Optionally, this can be assisted with one of the aforementioned axial attachment measures.

Advantageously, the difference between the outer diameter of the bearing outer ring and the bearing housing inner diameter required for vibration-inhibiting oil film formation is produced by a radial constriction of the carrier ring when it is pressed into the bearing housing. Thus, the bearing cartridge is preassembled and can be pressed by the user on site without any special knowledge of bearing construction, without losing any warranty claims.

In the aforementioned embodiment, the inner diameter of the carrier ring is variable by a radial force from the outside. Therefore, only a hole with a certain inner diameter is necessary for the placement of the bearing cartridge in the turbocharger housing, which is applied when pressing the bearing cartridge the necessary radial force to constrict the entire support ring and thus its inner diameter radially, d. H. to compress. Only then is the desired radial distance between the outer diameter of the bearing outer ring or a plurality of bearing outer rings and the carrier ring made.

It is considered that the centering of the bearing within the support ring is basically achieved by the rotation of the shaft during operation. Here, the unbalance of the shaft generates a bearing rotating outward radial force. With an eccentric position of the bearing within the oil film, that is, when the oil film has a different thickness along the circumference, the thicker part of the oil film causes less resistance to the radial force than the thinner part. The bearing in the cartridge moves in the direction of the lower resistance, ie the thicker part of the oil film and can compensate for the thickness difference with self-centering accordingly. Therefore, it is important that the geometry of the hollow cylindrical space for generating a uniform oil film by a radial constriction of the support ring when pressing it into a bearing housing is made exactly.

Now the oil supply for the squeeze film has to be ensured. This is done via the first groove, which rotates at least partially or completely in the circumferential direction. Ideally, the first groove has a ring shape. The first groove provides at the respective circumferential location for a transport of the lubricant in the circumferential direction to then guide the oil in the hollow cylindrical space between the carrier ring and outer ring, where it begins to migrate axially.

Advantageously, the first groove is formed on the cylindrical outer surface of the bearing outer ring and / or on the hollow cylindrical inner surface of the carrier ring. Since this is an area inaccessible to the user, there is a great deal of design freedom for the first groove, which contributes to optimizing the storage functionality.

Also, the bearing housing has a bore for oil supply, which is indirectly connected to the first groove via a supply bore of the support ring. In this case, it can be determined as required whether the supply of the intermediate space via the carrier ring should be vertical (for example from above or below) or horizontal. In the support ring, said supply bore or even a plurality of supply holes can be introduced at each circumferential location to open into the first groove. This is advantageous in that the intermediate space in which the squeeze film is formed is not accessible to a user. Thus, the manufacturer can provide appropriate guarantees, since possible vibration problems, then clearly factory must have arisen.

Furthermore, the number of supply holes is basically not limited. Preferably, a plurality of supply bores are correspondingly formed in the bearing housing, in the support ring and / or in the outer rings, which are available to supply the oil film.

Advantageously, the carrier ring is designed for pressing advantageous, d. H. he may have a radial flange or mounting flange, which can transmit axial Einpresskräfte optimally without burdening the bearing interior. After pressing in, the bearing cartridge is operable.

The bearing cartridge advantageously includes at least one bearing with a bearing inner and a bearing outer ring, between which a number of rolling elements is guided. The rolling elements are guided in Wälzkörperlaufbahnen, which are introduced on the outer circumference of the inner bearing ring or on the inner circumference of the outer bearing ring. Both bearing rings can be made either in one piece or two parts.

The bearing housing can be made of different materials. Due to the high loads during operation of a turbocharger, temperature-resistant and corrosion-resistant metallic materials are particularly suitable here.

The bearing may be formed as a rolling bearing. Here, for example, a configuration with held within a cage rolling elements as well as a vollkugelige variant without cage conceivable. With regard to the loads of the bearing unit and taking into account the operating conditions, such as temperature influences or corrosion, the bearing rings are made in particular of temperature and corrosion resistant materials. For example, hardened steels having a Vickers hardness of at least 600 HV are suitable for this purpose. The bearing rings have this hardness, in particular on their surface or at the points of Wälzkörperlaufbahnen.

Furthermore, a spray oil hole can be introduced in the bearing outer ring, which presses the oil from the first groove into the bearing interior. The oil can thus be used, for example, for the lubrication of the bearing components, wherein the position of the spray oil hole at the periphery is freely selectable.

To ensure the drainage of the oil, the bearing cartridge usually includes a drain groove on its outer periphery. This is communicatively connected to a bearing bore additionally introduced in the outlet bore. In this way, the oil supplied via the supply bore to the intermediate space can flow away continuously. The diameter of the outlet is for this purpose preferably dimensioned so that an undisturbed oil drain is possible. Furthermore, the oil can also flow in the axial direction outside between the bearing cartridge and the bearing housing.

In an advantageous embodiment of the invention, the supply bore opens for oil supply of the intermediate space substantially from below into the first groove. This embodiment supports the already mentioned above self-centering of the bearing cartridge within the bearing housing by a uniform oil film, since the oil pressure counteracts the gravitational force and thus the weight of the bearing cartridge.

The supply bore is preferably aligned in the bearing housing perpendicular to the bearing housing axis. Due to the vertical orientation, a uniform distribution of the oil in the intermediate space between the outer bearing ring and the bearing housing and thus a centering of the outer bearing ring and the bearing can be achieved. In principle, a vertical alignment is particularly advantageous if the oil passes directly from the supply bore into the intermediate space. In this case, a uniform distribution of the oil along the circumference of the outer bearing ring can be achieved in a simple manner via a vertically oriented supply bore.

Furthermore, the supply bore may preferably have a different cross section from the circular diameter and be used together with the outer bearing ring on its outer circumference circumferential groove as a pressure distribution chamber. This applies when using a carrier ring for this analog.

In a further advantageous embodiment of the invention, a pressure distribution chamber for oil supply of the intermediate space is additionally included. The pressure distribution chamber may in this case be introduced, for example, in the form of a recess in the bearing housing. Furthermore, additionally or alternatively, a pressure distribution chamber is possible, which results from a corresponding shape of the bearing cartridge. Here, for example, the outer bearing ring or the support ring may be flattened at one point of its circumference, so that when installing the bearing cartridge in a bearing housing, a free space at the location of the flattening arises, which is available as a pressure distribution chamber. The pressure distribution chamber can basically be designed to be flexible on the circumference of the outer bearing ring or of the carrier ring. In this case, the pressure-induced radial force on the bearing cartridge can be influenced overall by the targeted design and positioning of the pressure distribution chamber.

Appropriately, the position of the supply hole in the bearing housing for a second groove in the support ring on the periphery is freely selectable. The second groove in the support ring is preferably formed with a correspondingly large cross section, so that no significant pressure loss is recorded. Alternatively, the second groove in the carrier ring can be omitted if the bore for supplying the first groove is formed both axially and circumferentially at the same location as the supply bore in the bearing housing. The shape of the hole in the support ring can be designed arbitrarily in terms of their cross section and their shape and deviate from a circular shape.

Advantageously, the second, at least partially or completely extending in the circumferential direction groove formed in the support ring and communicating with the supply bore of the support ring. This makes it possible to transport the oil around the bearing in places that need to be supported with a certain oil flow, to prevent adverse thinning of the oil film. For this purpose, the second groove may in principle have a plurality of communicating connections with the first groove.

In all the aforementioned embodiments applies, as already mentioned, that the number of grooves is not limited. Preferably, the number of grooves corresponds to the number of supply holes communicating with them. Conveniently, further comprising a groove communicating with an outlet bore for the oil, so that the oil supplied via the or each supply bore to the intermediate space can flow away continuously. The bearing rings can of course also be in the use of a carrier ring one or more parts, so that the use of a spring element is also possible here.

Preferably, the bearing outer ring is made in two parts, wherein the two partial rings of the outer bearing ring are axially spaced apart. A two-part design allows for easy production of the partial rings and reduces the assembly costs of the storage unit. Furthermore, both the cost and the transport costs can be reduced. The axial spacing can be achieved axially, for example, by means of a spring element. The spring element presses apart the two partial rings and holds them so resiliently in the intended position. The axial distance of the partial rings to one another is given in this case in particular by the bias of the spring element. The spring element may be formed, for example, as a metallic spiral spring.

In a further advantageous embodiment of the invention, the bearing is designed as a rolling bearing. Rolling bearings are suitable for different storage cases and are used in particular for the fixation of waves, wherein they absorb the radial and axial forces while allowing the rotation of the shaft. Rolling bearings generally consist of two bearing rings with integrated raceways. Between the bearing rings rolling elements are arranged, which roll on the raceways. As rolling elements of common bearing types, for example, balls, cylindrical rollers, needle rollers or tapered rollers can be used depending on the requirement. Furthermore, training with a roller cage leading cage is possible.

More preferably, the bearing is designed as a sliding bearing. In a sliding bearing, the two parts moving relative to each other have direct contact and slide on their contact surfaces. A contact surface thus takes the place of a rolling body of the rolling bearing, being completely dispensed with the rolling elements. The resulting frictional resistance can be reduced in particular by the production of a lubricating film. Furthermore, a reduction in the frictional resistance can be achieved by choosing low-friction material pairings of the contacting parts. The use of a plain bearing for supporting a shaft of a turbocharger is suitable, for example, because the oil supplied via the supply bores can also be used to lubricate the plain bearing.

The support ring may conveniently be fixed non-positively or positively in the bearing housing. Due to the communicating connection between the supply bore and the circumferential circumferential groove of the support ring, the oil can be distributed in the groove over the circumference of the support ring. At the bottom of the carrier ring, the oil can pass through a hole connected to the groove in the groove on the outer circumference of the outer bearing ring, so that the oil film for vibration damping between the outer bearing ring and the carrier ring is formed. From the first groove becomes a part. the oil is then pressed into the bearing interior, for example via a spray oil hole connected to the groove, and is available for lubricating the bearing components.

In an advantageous embodiment, a positive and / or frictional connection between the carrier ring and the bearing outer ring is produced. By means of this rotation of the support ring and the bearing outer ring or the support ring and the two outer part rings are secured against each other. In particular, pins, bolts or sockets are suitable for this purpose. Bushings are characterized by their lightness and bolts by their simple structure. It is not absolutely necessary that the positive or non-positive locking of the anti-rotation device extends to the bearing housing, if the support ring is already pressed into this and thus non-positively is secured against rotation. In principle, however, both options are available, whereby the bearing outer ring can be secured both relative to the bearing housing and / or relative to the support ring against rotation.

Further advantageous embodiments and preferred developments of the invention can be taken from the description of the figures and / or the dependent claims.

Short description of the drawing

In the following the invention will be described and explained in more detail with reference to the exemplary embodiments illustrated in the figures.

Show it:

1 a turbocharger bearing cartridge disposed in a housing in vertical longitudinal section along the axis of rotation,

2 the turbocharger bearing cartridge off 1 in a horizontal longitudinal section along the axis of rotation,

3 the turbocharger bearing cartridge off 1 in a sectional view perpendicular to the axis of rotation,

4 a turbocharger bearing cartridge disposed in a housing with a radial outer flange in vertical longitudinal section along the axis of rotation,

5 the turbocharger bearing cartridge off 4 in a horizontal longitudinal section along the axis of rotation,

6 the turbocharger bearing cartridge off 4 in a sectional view perpendicular to the axis of rotation,

7 a turbocharger bearing cartridge arranged in a housing with a sleeve-like anti-twist device in vertical longitudinal section along the axis of rotation,

8th the turbocharger bearing cartridge off 7 in a horizontal longitudinal section along the axis of rotation,

9 the turbocharger bearing cartridge off 7 in a sectional view perpendicular to the axis of rotation,

10 a arranged in a housing turbocharger bearing cartridge with different outer diameters in the vertical longitudinal section along the axis of rotation,

11 the turbocharger bearing cartridge off 10 in a horizontal longitudinal section along the axis of rotation,

12 the turbocharger bearing cartridge off 10 in a sectional view perpendicular to the axis of rotation,

13 a turbocharger bearing cartridge arranged in a housing with split inner ring in vertical longitudinal section along the axis of rotation,

14 the turbocharger bearing cartridge off 13 in a horizontal longitudinal section along the axis of rotation, and

15 the turbocharger bearing cartridge off 13 in section perpendicular to the axis of rotation.

Detailed description of the drawing

1 to 3 each show the same bearing cartridge for a turbocharger in a vertical, horizontal longitudinal section and a section perpendicular to the axis of rotation R, wherein the direction of gravity extends in the vertical. The bearing cartridge is in an axially extending metallic bearing housing 15 arranged. As part of the bearing cartridge is designed as a double-row angular contact ball bearing, which has an outer bearing ring and an inner bearing ring 24 having. The outer bearing ring is with the two partial rings 13 . 14 executed in two parts and within the carrier ring 11 arranged. As rolling elements are between the bearing rings 13 . 14 . 24 Used bullets.

Between the outer surface of the outer part rings 13 . 14 and the carrier ring 11 a gap in the form of an annular gap is formed with an oil film. The oil film is installed when installed via two supply holes 25 supplied with oil. These are both supply holes 25 each with the outer part rings 13 . 14 with an outer circumference circumferential, first grooves 23 communicatively connected.

Furthermore, the outer partial rings offer 13 . 14 enough space in the middle so that the oil of the oil film runs around the circumference and if necessary via a drainage groove 35 into the outlet hole 26 whose diameter is dimensioned so that a trouble-free oil drain takes place and a consistent oil film can be ensured. In addition, the oil also flows in the axial direction, outside between the outer part rings 13 . 14 and the carrier ring 11 from.

The two partial rings 13 . 14 of the outer bearing ring are formed by means of a designed as a metallic coil spring spring element 40 axially spaced apart, so that the two partial rings 13 . 14 resiliently held in the intended position.

The bearing cartridge has a form-fitting and possibly also non-positively fixed in the bearing housing support ring 11 made of a metallic material. In the carrier ring 11 the warehouse is added. The carrier ring 11 is on its outer circumference with two circumferential, second grooves 22 provided with the supply holes 20 of the bearing housing 15 communicate communicatively. After insertion, or with additional adhesion after the non-positive pressing, the cartridge, consisting of the support ring 11 with incorporated turbocharger bearing, the carrier ring bumps 11 axially to the radial constriction 28 and is in the axial opposite direction through the fixing disc 27 axially locked, or fixed axially. Optionally, the inner radius of the carrier ring 11 radially compressed, bringing the radial distance to the outer surface of the partial rings 13 . 14 is dimensioned so that a vibration-inhibiting oil film can arise at a given oil flow.

The formation of the oil film is supported by the fact that both in the outer circumference of the partial rings 13 . 14 , as well as in the outer periphery of the carrier ring 11 second grooves 22 are introduced. In the second grooves 22 the oil spreads over the circumference of the carrier ring 11 , At the top of the carrier ring 11 or alternatively at another circumferential location (eg, below) are the second grooves 22 optionally by means of bores with the first grooves 23 connected, with the oil first in the second grooves 22 on the outer circumference of the partial rings 13 . 14 the outer bearing ring passes to be circumferentially redistributed and optionally at a circumferential location further radially to the first grooves 23 is directed. The oil film thus forms in the space between the outer partial rings 13 . 14 and the carrier ring 11 out.

Furthermore, the oil from the first grooves 23 in the partial rings 13 . 14 via a spray oil hole 30 pressed into the bearing interior and is available for lubrication of the bearing components. The drain of the oil is via a in the bearing housing 15 introduced outlet bore 26 guaranteed.

The bolt 17 provides as a rotation lock a positive connection between the carrier ring, housing 15 and the part rings 13 . 14 ago. At a bolt 17 with circular cross section, an axial force component is introduced by the angular relationships in the contact point in the support of the friction torque, the amount of which depends on the friction torque. In other words, at higher speeds is to be expected that the friction torque and thus the axial force on the Wellenaxialkraftabgewandten side increases, which reduces the risk of slipping with speed and friction torque.

For torsion-proof positioning of the bearing cartridge is still a with the bearing housing 15 fixed to the housing connected bolt 17 includes, in a hole in the carrier ring 11 is arranged.

4 to 6 each show the same, second bearing cartridge for a turbocharger in a vertical, horizontal longitudinal section and a section perpendicular to the axis of rotation R, wherein the direction of gravity in the vertical. The bearing cartridge is in an axially extending metallic bearing housing 16 arranged.

The pin 18 is solid and carrier firmly anchored in the cartridge. This is a positive connection between the carrier ring 12 and the part rings 13 . 14 produced. A special treatment of the housing 16 for attaching a rotation is not required. This is done either by the adhesion of the carrier ring 12 with the interior of the case 16 and / or by a fixation of the outer flange 19 on the housing 16 , for example, by means of screws or similar fasteners (not shown) accomplished.

The pin 18 can thus be preinstalled together with the entire cartridge factory and serve as a transport lock that holds the cartridge together so that they are easily inserted and on the outer flange 29 is screwed. Pressing in the cartridge with a clearance fit or over-fitting results in an additional adhesion. If this is large enough, then the screwing or the mounting flange is unnecessary 29 ,

During operation, the pin has 18 the task axial forces acting over the inner ring 24 introduced and via the rolling elements on the outer part ring 13 . 14 be supported. This will cause a tilting of the outer part rings 13 . 14 prevented.

The further detailed description of the individual components of the storage unit can in particular the description of the 1 to 3 be removed.

7 to 9 each show the same, third bearing cartridge for a turbocharger in a vertical, horizontal longitudinal section and a section perpendicular to the axis of rotation R, wherein the direction of gravity in the vertical. The bearing cartridge is in an axially extending metallic bearing housing 16 arranged.

The sockets 19 allow through their hollow cylindrical shape an undisturbed oil drain, the bushes 19 continue to perform the same functions as the pin 18 out 4 , However, the use of two diametrically opposed bushes 19 prevents axial forces from tilting the outer part rings 13 . 14 within the carrier ring 12 Perform by applying an axial force to the inner ring 24 , about the balls on the sub-rings 13 . 14 is transmitted, at least at two circumferential locations in the carrier ring 12 is derivable.

The further detailed description of the individual components of the storage unit can in particular the description of the 1 to 3 respectively 4 to 6 be removed.

10 to 12 each show the same, fourth bearing cartridge for a turbocharger in a vertical, horizontal longitudinal section and a section perpendicular to the axis of rotation R, wherein the direction of gravity extends in the vertical. The bearing cartridge is in an axially extending metallic bearing housing 16 arranged.

The further detailed description of the individual components of the storage unit can in particular the description of the 1 to 3 respectively 7 to 9 be removed.

13 to 15 each show the same, fifth bearing cartridge for a turbocharger in a vertical, horizontal longitudinal section and a section perpendicular to the axis of rotation R, wherein the direction of gravity in the vertical. The bearing cartridge is in an axially extending metallic bearing housing 16 arranged.

The outer ring 34 is in one piece and the inner ring as two inner part rings 31 . 32 executed. In this case, a spring preload can be omitted. However, the flow of the draining oil is hindered by this, which is why another drain groove 36 on the one-piece bearing outer ring 34 necessary is. Thus, the oil can always migrate axially until it enters one of the drain grooves 35 . 36 passes through and through the lower socket 19 finally into the outlet hole 26 flow.

Further, the carrier ring 33 , as in the previous embodiment, fastened exclusively non-positively, so does not require any further fastening means. The strength of the frictional connection is in principle, as already indicated, possible by an adaptation of the negative clearance, but can also on the outer surface of the carrier ring 33 non-positive areas 37 , such as four annular, frictional areas 37 , be provided with a certain outer diameter. About the axial extent of the annular regions, the fastening force is adjustable and can be adjusted according to the required holding force in turbocharger operation. The number of frictional areas is variable.

Due to the exact fixability of the frictional connection and thus the force necessary for pressing force is the end face of the carrier ring 33 flush with the front of the housing 16 be pressed. Since the reference surfaces are easy to apply, the installation is much easier.

The further detailed description of the individual components of the storage unit can be found in particular the description of 1 to 3 respectively 10 to 12 be removed.

In summary, the invention relates to a bearing cartridge for a turbocharger, comprising a in a bearing housing 15 . 16 Press-in carrier ring 11 . 12 . 33 and one from the carrier ring 11 . 12 . 33 radially enclosed bearing outer ring 13 . 14 . 34 , wherein between the cylindrical outer surface of the bearing outer ring 13 . 14 . 34 and the hollow cylindrical inner surface of the carrier ring 11 . 12 . 33 a space filled with oil is formed and the support ring 11 . 12 . 33 a supply bore formed for oil supply of the gap 25 having, wherein the supply bore 25 with a circumferentially circumferential and at least partially formed by the bearing outer ring, the first groove 23 is communicatively connected. A user-friendly, portable and factory-installable turbocharger bearing cartridge is to be specified. This is solved by the bearing outer ring 13 . 14 . 34 has at least one rolling element raceway and the support ring 11 . 12 . 33 can be fastened in the bearing housing. The result is an efficient, factory pre-assembled turbocharger bearing cartridge with a low number of components.

LIST OF REFERENCE NUMBERS

R

axis of rotation

X

Horizontal axis

Y

vertical axis

11

support ring

12

support ring

13

outer part ring

14

outer part ring

15

bearing housing

16

bearing housing

17

bolt

18

Pin code

19

Rifle

20

supply hole

22

second groove

23

first groove

24

Bearing inner ring

25

drilling

26

outlet bore

27

affixation

28

radial narrowing

29

outer flange

30

Oil-drilling

31

inner part ring

32

inner part ring

33

support ring

34

Bearing outer ring

35

drain groove

36

drain groove

37

non-positive area

40

spring element

QUOTES INCLUDE IN THE DESCRIPTION

This list of the documents listed by the applicant has been generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Cited patent literature

• DE 3617402 A1 [0005]

Claims (12)

Bearing cartridge for a turbocharger, comprising one in a bearing housing ( 15 . 16 ) mountable carrier ring ( 11 . 12 . 33 ) and one of the carrier ring ( 11 . 12 . 33 ) radially encompassed, at least one Wälzkörperlaufbahn having bearing outer ring ( 13 . 14 . 34 ), wherein between the cylindrical outer surface of the bearing outer ring ( 13 . 14 . 34 ) and the inner surface of the carrier ring ( 11 . 12 . 33 ) is formed filled with vibration-inhibiting oil gap and the support ring ( 11 . 12 . 33 ) a supply bore formed for oil supply of the intermediate space ( 25 ), wherein the supply bore ( 25 ) with a peripheral circumferential and at least partially from the bearing outer ring ( 13 . 14 . 34 ), first groove ( 23 ) is communicatively connected. Bearing cartridge according to claim 1, wherein the support ring ( 11 . 12 . 33 ) in the bearing housing ( 15 . 16 ) is fastened by means of a radial clearance fit or a radial transition fit. Bearing cartridge according to claim 2, wherein the bearing outer ring ( 13 . 14 . 34 ) an outer diameter and the carrier ring ( 11 . 12 . 33 ) have an inner diameter, wherein the vibration-inhibiting oil film formation required difference between the two diameters by a radial constriction of the support ring ( 11 . 12 . 33 ) when it is pressed into a bearing housing ( 15 . 16 ) can be produced. Bearing cartridge according to one of the preceding claims, wherein the carrier ring ( 12 ) a mounting flange ( 19 ) for mounting on the bearing housing ( 16 ) having. Bearing cartridge according to one of the preceding claims, wherein the first groove ( 23 ) on the cylindrical outer surface of the bearing outer ring ( 13 . 14 . 34 ) and / or on the inner surface of the carrier ring ( 11 . 12 . 33 ) is trained. Bearing cartridge according to one of the preceding claims, wherein one in the first groove ( 23 ) opening spray oil hole in the bearing outer ring ( 13 . 14 . 34 ) is introduced. Bearing cartridge according to claim 6, wherein the bearing cartridge has a bearing designed as a rolling bearing, in particular as a multi-row roller bearing, and the spray oil hole is provided for oil supply of rolling rolling elements of the rolling bearing. Bearing cartridge according to one of the preceding claims, wherein a second, at least partially extending in the circumferential direction groove ( 22 ) in the carrier ring ( 11 . 12 . 33 ) and with the supply bore ( 25 ) is communicatively connected. Bearing cartridge according to one of the preceding claims, wherein a bearing inner ring ( 24 ) in one piece and the bearing outer ring are made in two parts, and the two outer partial rings ( 13 . 14 ) axially, in particular by means of a spring element ( 40 ), are spaced from each other. Bearing cartridge according to one of the preceding claims 1 to 9, wherein the bearing outer ring ( 34 ) in one piece and the bearing inner ring ( 31 . 32 ) is made in two parts. Bearing cartridge according to one of the preceding claims, wherein the carrier ring ( 11 . 12 . 33 ) and the bearing outer ring ( 34 ) or the carrier ring ( 11 . 12 . 33 ) and the two outer partial rings ( 13 . 14 ) by means of an anti-twist device ( 17 . 18 . 19 ), in particular by a pin ( 18 ), a bolt ( 17 ) or a rifle ( 19 ), secured against rotation to each other. Bearing cartridge according to claim 12, wherein the bearing outer ring ( 13 . 14 . 34 ) relative to the bearing housing ( 15 ) and / or relative to the carrier ring ( 12 . 33 ) is secured against twisting.

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