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WO2012079879A1 - Cartouche de palier pour un turbocompresseur - Google Patents

Cartouche de palier pour un turbocompresseur Download PDF

Info

Publication number
WO2012079879A1
WO2012079879A1 PCT/EP2011/070044 EP2011070044W WO2012079879A1 WO 2012079879 A1 WO2012079879 A1 WO 2012079879A1 EP 2011070044 W EP2011070044 W EP 2011070044W WO 2012079879 A1 WO2012079879 A1 WO 2012079879A1
Authority
WO
WIPO (PCT)
Prior art keywords
bearing
ring
oil
cartridge according
outer ring
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/EP2011/070044
Other languages
German (de)
English (en)
Inventor
Heiko Schmidt
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Schaeffler Technologies AG and Co KG
Original Assignee
Schaeffler Technologies AG and Co KG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Schaeffler Technologies AG and Co KG filed Critical Schaeffler Technologies AG and Co KG
Publication of WO2012079879A1 publication Critical patent/WO2012079879A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
    • F01D25/16—Arrangement of bearings; Supporting or mounting bearings in casings
    • F01D25/162—Bearing supports
    • F01D25/164—Flexible supports; Vibration damping means associated with the bearing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
    • F02C6/00—Plural gas-turbine plants; Combinations of gas-turbine plants with other apparatus; Adaptations of gas-turbine plants for special use
    • F02C6/04—Gas-turbine plants providing heated or pressurised working fluid for other apparatus, e.g. without mechanical power output
    • F02C6/10—Gas-turbine plants providing heated or pressurised working fluid for other apparatus, e.g. without mechanical power output supplying working fluid to a user, e.g. a chemical process, which returns working fluid to a turbine of the plant
    • F02C6/12—Turbochargers, i.e. plants for augmenting mechanical power output of internal-combustion piston engines by increase of charge pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C25/00—Bearings for exclusively rotary movement adjustable for wear or play
    • F16C25/06—Ball or roller bearings
    • F16C25/08—Ball or roller bearings self-adjusting
    • F16C25/083—Ball or roller bearings self-adjusting with resilient means acting axially on a race ring to preload the bearing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C27/00—Elastic or yielding bearings or bearing supports, for exclusively rotary movement
    • F16C27/04—Ball or roller bearings, e.g. with resilient rolling bodies
    • F16C27/045—Ball or roller bearings, e.g. with resilient rolling bodies with a fluid film, e.g. squeeze film damping
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/66—Special parts or details in view of lubrication
    • F16C33/6637—Special parts or details in view of lubrication with liquid lubricant
    • F16C33/6659—Details of supply of the liquid to the bearing, e.g. passages or nozzles
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C35/00—Rigid support of bearing units; Housings, e.g. caps, covers
    • F16C35/04—Rigid support of bearing units; Housings, e.g. caps, covers in the case of ball or roller bearings
    • F16C35/06—Mounting or dismounting of ball or roller bearings; Fixing them onto shaft or in housing
    • F16C35/07—Fixing them on the shaft or housing with interposition of an element
    • F16C35/077—Fixing them on the shaft or housing with interposition of an element between housing and outer race ring
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
    • F16C19/18—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls
    • F16C19/181—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact
    • F16C19/183—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles
    • F16C19/184—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles in O-arrangement
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2360/00—Engines or pumps
    • F16C2360/23—Gas turbine engines
    • F16C2360/24—Turbochargers

Definitions

  • 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 in the intermediate space has a supply bore, wherein the supply bore is connected in a communicating manner with a first groove running around in the peripheral direction and formed at least partially by the bearing outer ring.
  • 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.
  • 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.
  • 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 increase allows the use of a more powerful motor with approximately the same dimensions or, alternatively, allows a reduction in motor dimensions, ie achieving comparable performance in smaller and lighter machines.
  • the shaft rotates at high engine speed as the engine speed increases. Due to the high rotational speed, vibrations caused by the rotation of the shaft, for example, can be transmitted to the bearing cartridge.
  • vibrations caused by the rotation of the shaft for example, can be transmitted to the bearing cartridge.
  • usually storage units are used, which can dampen the vibrations occurring by a so-called Quetschölfilm.
  • 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.
  • turbocharger bearing cartridges which have a bearing with multi-part outer ring and are arranged in a carrier ring. There is also a so-called squeeze film designed for vibration inhibition.
  • 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.
  • a corresponding decoupling device is needed, which requires a large number of parts and is therefore expensive.
  • turbocharger bearing cartridge which is easy to handle in comparison to the prior art and which has a low number of components but equally has the usual advantages of known turbocharger bearing cartridges.
  • 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 WälzSystemterrorismbahn and the support ring in the bearing housing can be fastened.
  • the bearing outer ring is radially encompassed by the carrier ring, wherein between the zyrnrischen outer surface of the bearing outer ring and the inner surface of the carrier 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 first groove running around in the circumferential direction and formed at least partially by the bearing outer ring. He leads oil from the bearing housing further radially inward to the camp.
  • the bearing cartridge can be secured in the bearing housing by means of a radial clearance fit or a radial transition fit.
  • a clearance fit would be implemented by an appropriate choice of the outer diameter of the carrier ring.
  • the outer diameter of the carrier ring is slightly larger than the inner diameter of the bearing housing. Therefore, a pressing of the bearing cartridge would indeed necessary, but would also provide other security devices, such as, for example, an axial fixation or clamping or attachment of the carrier ring via a provided on the support ring Make mounting flange superfluous.
  • an axial fixation or clamping or attachment of the carrier ring via a provided on the support ring Make mounting flange superfluous 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.
  • 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.
  • 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.
  • 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.
  • the difference between the outer diameter of the bearing outer ring and of the bearing housing inner diameter required for the vibration-inhibiting formation of oil film is produced by a radial constriction of the carrier ring when it is pressed into the bearing housing.
  • 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 carrier ring and thus its inner diameter radially, ie to compress. Only then is the desired radial distance between outside di- knife of the bearing outer ring or more bearing outer rings and the carrier ring produced.
  • the centering of the bearing within the carrier ring is basically achieved by the rotation of the shaft during operation.
  • the unbalance of the shaft generates a bearing rotating outward radial force.
  • 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.
  • the oil supply for the squeeze film has to be ensured. This is accomplished via the first groove, which rotates at least partially or completely in the circumferential direction.
  • 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.
  • 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 that is inaccessible to the user, there is a great deal of design freedom for the first groove, which contributes to the optimization of the warehouse functionality.
  • the bearing housing also has a bore for oil supply, which is connected indirectly to the first groove via a supply bore of the carrier ring. that is.
  • a supply bore of the carrier ring 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.
  • said supply bore or else a plurality of supply bores can be introduced at each circumferential part in order 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.
  • the manufacturer can provide appropriate guarantees, since possible vibration problems, then clearly factory must have arisen.
  • the number of supply holes is basically not limited.
  • a plurality of supply bores are accordingly formed in the bearing housing, in the carrier ring and / or in the outer rings, which are available for supplying the oil film.
  • the carrier ring is designed for pressing advantageous, i. he may have a radial flange or mounting flange, which can transmit axial Einpresser 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 WälzEffbahnen, 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.
  • 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 WälzEffbahnen.
  • 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 also be used, for example, for lubricating the bearing components, wherein the position of the spray oil bore can be freely selected on the circumference.
  • the bearing cartridge usually includes a drain groove on its outer periphery. This is communicatively connected to an outlet bore additionally introduced in the bearing housing. 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.
  • 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.
  • 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 aligned supply bore.
  • 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 Druckver republics- chamber. This applies when using a carrier ring for this analog.
  • 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.
  • a pressure distribution chamber is possible, which results from a corresponding shape of the bearing cartridge.
  • 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.
  • the pressure-induced radial force can be influenced on the bearing cartridge by the targeted design and positioning of the pressure distribution chamber.
  • 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 carrier ring is preferably formed with a correspondingly large cross section, so that no significant pressure loss is recorded.
  • 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.
  • the second at least partially or entirely extending in the circumferential direction groove formed in the support ring and communicating with the supply bore of the support ring.
  • the second groove may in principle have a plurality of communicating connections with the first groove.
  • the number of grooves is not limited.
  • the number of grooves corresponds to the number of supply holes communicating with them.
  • a groove is included, which communicates 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.
  • 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 spacing of the partial rings relative to one another is given in particular by the prestressing of the spring element.
  • the spring element may be formed, for example, as a metallic spiral spring.
  • 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.
  • 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.
  • the bearing is designed as a sliding bearing.
  • a sliding bearing the two parts which move relative to one another 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.
  • 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 carrier ring in the circumferential direction circumferential groove For example, the oil may spread in the groove over the circumference of the carrier 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, a part of the oil is then pressed, for example via a connected with the groove oil splash in the bearing interior and is available for lubrication of the bearing components.
  • a positive and / or frictional connection between the carrier ring and the bearing outer ring is produced.
  • 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 rotation extends to the bearing housing, if the support ring is already pressed into this and thus is secured non-positively against rotation. In principle, however, both options are available, with which the bearing outer ring can be secured both relative to the bearing housing and / or relative to the support ring against rotation.
  • the turbocharger bearing cartridge of FIG. 1 in a horizontal longitudinal section along the axis of rotation, the turbocharger bearing cartridge of FIG. 1 in a sectional view perpendicular to the axis of rotation, arranged in a housing turbocharger bearing cartridge with radial outer flange in the vertical 4 in a horizontal longitudinal section along the axis of rotation, the turbocharger bearing cartridge of FIG. 4 in a sectional view perpendicular to the axis of rotation, arranged in a housing turbocharger bearing cartridge with a sleeve-like rotation in vertical longitudinal section along the axis of rotation, the turbocharger bearing cartridge from Fig. 7 in a horizontal longitudinal section along the axis of rotation,
  • FIG. 9 shows the turbocharger bearing cartridge of FIG. 7 in a sectional view perpendicular to the axis of rotation
  • FIG. a turbocharger bearing cartridge arranged in a housing with different outer diameters in a vertical longitudinal section along the axis of rotation
  • the turbocharger bearing cartridge of FIG. 10 in a horizontal longitudinal section along the axis of rotation
  • the turbocharger bearing cartridge of FIG. 10 in a sectional view perpendicular to the axis of rotation
  • Fig. 14 the turbocharger bearing cartridge of FIG. 13 in a horizontal
  • Fig. 15 the turbocharger bearing cartridge of FIG. 13 in a sectional view perpendicular to the axis of rotation.
  • Figures 1 to 3 respectively 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 arranged in an axially extending metallic bearing housing 15.
  • 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.
  • the outer bearing ring is designed in two parts with the two partial rings 13, 14 and arranged inside the carrier ring 11.
  • As rolling elements are used between the bearing rings 13,14,24 balls.
  • a gap in the form of an annular gap is formed with an oil film.
  • the oil film is supplied in the installed state via two supply holes 25 with oil.
  • both supply bores 25 are connected in each case communicating with the outer partial rings 13, 14 with an outer circumference, first grooves 23.
  • the outer part rings 13,14 provide enough space in the middle, so that the oil of the oil film run circumferentially and optionally pass through a drain groove 35 in 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 ,
  • the oil also flows in the axial direction, outside between the outer partial rings 13,14 and the support ring 11.
  • the two partial rings 13, 14 of the outer bearing ring are axially spaced apart from one another by means of a spring element 40 designed as a metallic spiral spring, so that the two partial rings 13, 14 are resiliently held in the intended position.
  • the bearing cartridge has a form-fitting and possibly also frictionally fixed in the bearing housing carrier ring 1 1 made of a metallic material.
  • the bearing is added.
  • the carrier ring 1 1 is provided on its outer circumference with two circumferential, second grooves 22 communicating with the supply bores 20 of the bearing housing 15 communicating.
  • the cartridge consisting of the support ring 1 1 with turbocharger bearing contained, abuts the support ring 1 1 axially to the radial constriction 28 and is axially countered in the axial opposite direction by the fixing plate 27 , or fixed axially.
  • the inner radius of the support ring 1 1 is radially compressed, whereby the radial distance to the outer surface of the partial rings 13,14 is dimensioned such 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 in the outer periphery of the partial rings 13,14, as well as in the outer periphery of the carrier ring 1 1 second grooves 22 are introduced. In the second grooves 22, the oil distributed over the circumference of the carrier ring 1 1.
  • the second grooves 22 are optionally connected by means of bores with the first grooves 23, wherein the oil first passes into the second grooves 22 on the outer circumference of the partial rings 13, 14 of the outer bearing ring so as to be redistributed circumferentially and, if appropriate, is conducted further radially at a peripheral point to the first grooves 23.
  • the oil film thus forms in the space between the outer partial rings 13,14 and the carrier ring 1 1.
  • the oil is pressed by the first grooves 23 in the sub-rings 13,14 via a respective injection oil bore 30 in the bearing interior and is available for lubrication of the bearing components.
  • the drainage of the oil is ensured via an introduced in the bearing housing 15 outlet bore 26.
  • the bolt 17 provides a rotational lock a positive connection between the carrier ring, housing 15 and the partial rings 13,14 ago.
  • 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 it is to be expected that the friction torque and thus the axial force on the side facing away from the shaft axial force increases, which reduces the danger of slipping which increases with speed and friction torque.
  • a bolt 17 fixed to the housing and connected to the bearing housing 15 is furthermore included, which is arranged in a bore in the carrier ring 11.
  • Figures 4 to 6 respectively 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 extends in the vertical.
  • the bearing cartridge is arranged in an axially extending metallic bearing housing 16.
  • the pin 18 is solid and carrier firmly anchored in the cartridge. For a positive connection between the carrier ring 12 and the partial rings 13,14 is produced. A special processing of the housing 16 for attaching a VerFêt- tion is not required. This is done either by the adhesion of the support ring 12 to the interior of the housing 16 and / or by a fixation of the outer flange 19 on the housing 16, for example by means of screws or similar fastening means (not shown).
  • the pin 18 can thus be preinstalled at the factory together with the entire cartridge and serve as a transport lock, which holds the cartridge together in such a way that it is inserted without great effort and bolted to the outer flange 29. Pressing in the cartridge with a clearance fit or over-fitting results in an additional adhesion. If this is large enough, it is unnecessary to screw or the mounting flange 29th
  • the pin 18 has the task of supporting axial forces which are introduced via the inner ring 24 and transmitted via the rolling elements to the outer partial ring 13, 14. This prevents tilting of the outer partial rings 13, 14.
  • FIGS. 7 to 9 respectively show the same, third bearing cartridge for a turbocharger in a vertical, horizontal longitudinal section and a section of vertical right to the axis of rotation R, where the direction of gravity is vertical.
  • the bearing cartridge is arranged in an axially extending metallic bearing housing 16.
  • the bushings 19 allow through their hollow cylindrical shape undisturbed oil drain, wherein the bushings 19 continue to perform the same functions, as well as the pin 18 of FIG. 4.
  • the use of two diametrically opposed bushes 19 prevents axial forces to tilt the outer partial rings 13,14 lead within the support ring 12 by an axial force which is transmitted to the inner ring 24, via the balls on the partial rings 13,14, at least at two circumferential locations in the support ring 12 can be derived.
  • Figures 10 to 12 respectively 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 arranged in an axially extending metallic bearing housing 16.
  • Figures 13 to 15 respectively 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 extends in the vertical.
  • the bearing cartridge is arranged in an axially extending metallic bearing housing 16.
  • the outer ring 34 is in one piece and the inner ring as two inner partial rings 31, 32 executed. In this case, a spring preload can be omitted.
  • the flow of the draining oil is hindered by this, which is why a further drain groove 36 on the one-piece bearing outer ring 34 is necessary.
  • the oil can always migrate axially until it enters one of the drain grooves 35,36 and finally flow through the lower sleeve 19 into the outlet bore 26.
  • the carrier ring 33 is fastened exclusively in a non-positively locking manner, thus requiring no further fastening means.
  • the strength of the frictional connection is fundamentally possible, as already indicated, by adaptation of the negative clearance, however, force-locking regions 37, such as, for example, four annular frictional regions 37, with a specific outer diameter, can also be provided on the outer surface of the carrier ring 33.
  • the fastening force can be regulated via the axial extent of the annular regions and can be adjusted according to the holding force required in turbocharger operation.
  • the number of frictional areas is variable.
  • the end face of the carrier ring 33 can be pressed in flush with the end face of the housing 16. Since the reference surfaces are easy to apply, the installation is much easier.
  • the invention relates to a bearing cartridge for a turbocharger, comprising a be pressed into a bearing housing 15,16 carrier ring 1 1, 12,33 and a radially surrounded by the support ring 1 1, 12,33 bearing outer ring 13,14,34, wherein between the cylindrical outer surface of the outer bearing ring 13,14,34 and the hollow cylindrical inner surface of the carrier ring 1 1, 12,33 is formed with an oil-filled gap and the support ring 11, 12,33 a for the oil supply of the intermediate space formed supply bore 25, wherein the supply bore 25 communicating with a circumferentially circumferential and at least partially formed by the bearing outer ring, the first groove 23 is connected.
  • the aim is to provide a user-friendly, portable and factory-installed turbocharger bearing cartridge.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • General Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Supercharger (AREA)

Abstract

L'invention concerne une cartouche de palier pour un turbocompresseur, comprenant une bague de support (11, 12, 13) pouvant être introduite par pression dans un logement de palier (15, 16) et une bague de palier extérieure (13, 14, 34) entourée radialement par la bague de support (11, 12, 33). Dans ce cadre, un espace intermédiaire rempli d'huile est réalisé entre la surface extérieure cylindrique de la bague de palier extérieure (13, 14, 34) et la surface intérieure cylindrique creuse de la bague de support (11, 12, 33), et la bague de support (11, 12, 33) comporte un alésage d'alimentation (25) réalisé pour alimenter en huile l'espace intermédiaire, l'alésage d'alimentation (25) étant relié en communication à une première rainure (23) s'étendant dans la direction périphérique et formée au moins en partie par la bague de palier extérieure. L'invention vise à proposer une cartouche de palier pour un turbocompresseur facile à utiliser, transportable et pouvant être pré-installée en usine. A cet effet, la bague de palier extérieure (13, 14, 24) comporte au moins une piste de roulement pour corps de roulement et la bague de support (11, 13, 33) peut être fixée dans le logement de palier. On obtient ainsi avec un nombre réduit de pièces une cartouche de palier pour turbocompresseur performante, pouvant être prémontée en usine.
PCT/EP2011/070044 2010-12-17 2011-11-14 Cartouche de palier pour un turbocompresseur Ceased WO2012079879A1 (fr)

Applications Claiming Priority (2)

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DE102010054904A DE102010054904A1 (de) 2010-12-17 2010-12-17 Lagerkartusche für einen Turbolader
DE102010054904.5 2010-12-17

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Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2014009050A1 (fr) * 2012-07-09 2014-01-16 Schaeffler Technologies AG & Co. KG Roulement pour un turbocompresseur
EP2886318A1 (fr) * 2013-12-19 2015-06-24 Aktiebolaget SKF Conception de palier de centrage robuste à lubrification automatique et procédé d'utilisation
WO2015091886A1 (fr) * 2013-12-19 2015-06-25 Aktiebolaget Skf Conception de palier de centreur solide auto-lubrifiant et procédé d'utilisation
CN108006182A (zh) * 2017-12-28 2018-05-08 洛阳众悦精密轴承有限公司 一种用于滚珠丝杠的轴承支撑装置
CN114607700A (zh) * 2022-03-25 2022-06-10 中国航发哈尔滨东安发动机有限公司 一种适用于航空发动机轴承的减振及润滑装置

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DE102014209428A1 (de) 2014-05-19 2015-11-19 Schaeffler Technologies AG & Co. KG Lagerring für ein Radialwälzlager
DE102014209642A1 (de) 2014-05-21 2015-11-26 Schaeffler Technologies AG & Co. KG Lageraußenring für ein Radialwälzlager und Radialwälzlager
DE102014212620B4 (de) 2014-06-30 2019-02-14 Schaeffler Technologies AG & Co. KG Radialwälzlager eines Abgasturboladers
DE102015203414A1 (de) 2015-02-26 2016-09-01 Schaeffler Technologies AG & Co. KG Lageranordnung für einen Abgasturbolader
DE102015213176A1 (de) * 2015-07-14 2017-01-19 Continental Automotive Gmbh Lageranordnung für eine Welle
DE102016202319A1 (de) 2016-02-16 2017-08-17 Schaeffler Technologies AG & Co. KG Lagervorrichtung
DE102020114015B3 (de) * 2020-05-26 2021-06-10 Schaeffler Technologies AG & Co. KG Turbomaschine für einen Verbrennungsmotor

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FR2569771A1 (fr) * 1984-09-03 1986-03-07 Ishikawajima Harima Heavy Ind Dispositif de support pour turbochargeur pour permettre d'obtenir une rotation stable d'un arbre de turbine
US4756673A (en) * 1984-09-03 1988-07-12 Ishikawajima-Harima Jukogyo Kabushiki Kaisha Turbocharger
DE3617402A1 (de) 1985-05-30 1986-12-04 Teledyne Industries, Inc., Los Angeles, Calif. Turbolader mit einem vorgespannten lager
US4708602A (en) * 1985-05-30 1987-11-24 Teledyne Industries, Inc. Lubrication system for a turbocharger
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EP2141373A1 (fr) * 2007-05-01 2010-01-06 JTEKT Corporation Dispositif de palier pour turbocompresseur

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2014009050A1 (fr) * 2012-07-09 2014-01-16 Schaeffler Technologies AG & Co. KG Roulement pour un turbocompresseur
US9523389B2 (en) 2012-07-09 2016-12-20 Schaeffler Technologies AG & Co. KG Rolling bearing for a turbocharger
EP2886318A1 (fr) * 2013-12-19 2015-06-24 Aktiebolaget SKF Conception de palier de centrage robuste à lubrification automatique et procédé d'utilisation
WO2015091886A1 (fr) * 2013-12-19 2015-06-25 Aktiebolaget Skf Conception de palier de centreur solide auto-lubrifiant et procédé d'utilisation
CN108006182A (zh) * 2017-12-28 2018-05-08 洛阳众悦精密轴承有限公司 一种用于滚珠丝杠的轴承支撑装置
CN108006182B (zh) * 2017-12-28 2024-12-24 洛阳众悦精密轴承有限公司 一种用于滚珠丝杠的轴承支撑装置
CN114607700A (zh) * 2022-03-25 2022-06-10 中国航发哈尔滨东安发动机有限公司 一种适用于航空发动机轴承的减振及润滑装置
CN114607700B (zh) * 2022-03-25 2023-11-24 中国航发哈尔滨东安发动机有限公司 一种适用于航空发动机轴承的减振及润滑装置

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