WO2012079788A1 - Unité de palier pour turbocompresseur - Google Patents

Unité de palier pour turbocompresseur Download PDF

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Publication number
WO2012079788A1
WO2012079788A1 PCT/EP2011/065895 EP2011065895W WO2012079788A1 WO 2012079788 A1 WO2012079788 A1 WO 2012079788A1 EP 2011065895 W EP2011065895 W EP 2011065895W WO 2012079788 A1 WO2012079788 A1 WO 2012079788A1
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WO
WIPO (PCT)
Prior art keywords
bearing
ring
oil
bearing unit
housing
Prior art date
Application number
PCT/EP2011/065895
Other languages
German (de)
English (en)
Inventor
Heiko Schmidt
Original Assignee
Schaeffler Technologies AG & 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 & Co. KG filed Critical Schaeffler Technologies AG & Co. KG
Publication of WO2012079788A1 publication Critical patent/WO2012079788A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • 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
    • 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
    • F16C41/00—Other accessories, e.g. devices integrated in the bearing not relating to the bearing function as such
    • F16C41/04—Preventing damage to bearings during storage or transport thereof or when otherwise out of use
    • 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
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/02—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems
    • F16F15/023—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using fluid means
    • F16F15/0237—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using fluid means involving 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
    • 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
    • F16C19/16—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 a single row of balls
    • F16C19/163—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 a single row of balls with angular contact
    • 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
    • F16C19/54—Systems consisting of a plurality of bearings with rolling friction
    • F16C19/541—Systems consisting of juxtaposed rolling bearings including at least one angular contact bearing
    • F16C19/542—Systems consisting of juxtaposed rolling bearings including at least one angular contact bearing with two rolling bearings with angular contact
    • F16C19/543—Systems consisting of juxtaposed rolling bearings including at least one angular contact bearing with two rolling bearings with angular contact 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
    • 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

Definitions

  • the invention relates to a bearing unit for a turbocharger, comprising a bearing housing extending in an axial direction, a bearing cartridge arranged within the bearing housing with a carrier ring, and a bearing positioned in this bearing with an outer bearing ring, wherein between the bearing housing and the bearing cartridge Space is formed for a vibration-damping oil film, and wherein the support ring has a bore communicating with a formed in the outer bearing ring spray oil hole for bearing lubrication in conjunction.
  • a turbocharger typically serves 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 with each intake stroke more oxygen enters the combustion chamber of the engine.
  • 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 individual bearing components.
  • the individual bearing components Basically serves formed in the space between the outer bearing ring and the bearing housing so-called Quetschölfilm to dampen these vibrations and thus to prevent contact between the bearing components.
  • the supply of the individual bearing components with oil is absolutely necessary. For this purpose, a portion of the oil from the Quetschölfilm starting from the intermediate space is metered into the bearing interior. In this way, basically an approximately frictionless and undisturbed mileage of the bearing used can be made possible.
  • the bearing unit comprises a bearing cartridge which is arranged within a bearing housing and which is designed as a bearing device, and also a bearing ring designed as a bearing carrier.
  • the bearing cartridge includes two ball bearings and an outer bearing ring. Between the outer periphery of the outer bearing ring and the inner wall of the bearing housing, an oil film is formed, which serves to dampen vibrations during operation of the turbocharger.
  • the bearing support a bore and the outer bearing ring on a trained as a feed passage spray oil hole, which is connected for the transmission of lubricating fluid with the bearing components in the bearing interior.
  • a bearing unit for a turbocharger comprising a bearing housing extending in an axial direction, a bearing cartridge arranged within the bearing housing with a carrier ring and a bearing positioned therein with an outer bearing ring, wherein between the bearing housing and the bearing cartridge is formed with a space for a vibration damping oil film, and wherein the support ring has a bore communicating with a bearing oil bore formed in the outer bearing ring for bearing lubrication. It is provided that the position of the outer bearing ring and the position of the spray oil hole are fixed against rotation relative to the bore in the carrier ring by means of a securing element.
  • the invention takes into account that the oil supply of the bearing components in the bearing interior so far can be done only insufficiently accurate.
  • the spray oil hole to pressurize the bearing interior is not rotationally at a fixed position, resulting in the spray oil drilling a variable pressure at the same supply oil pressure.
  • a permanently uniform oil supply of the bearing interior is therefore not feasible so far.
  • the invention recognizes that this problem can be overcome if the spray oil hole is fixed against rotation relative to the bore in the carrier ring by means of a securing element.
  • Both the spray oil holes and the holes in the carrier ring can be introduced according to requirements at different locations along the circumference of the carrier ring and the outer bearing ring. This can be adjusted in particular by the vote of the positions and the cross sections of the spray oil hole and the bore in the support ring of the supply oil pressure at the spray oil hole.
  • the bore in the carrier ring as well as the spray oil hole can have different diameters according to the required amount of oil and are suitably matched to one another.
  • the bore in the carrier ring can be formed along the circumference at the same point as the spray oil bore in the outer bearing ring, so that the flow of the oil to be metered into the bearing interior can take place almost unhindered.
  • the spray oil hole can also be introduced at a position that is different in the installed state of the bore in the carrier ring.
  • the oil must have a Travel along the circumference of the carrier ring and / or the outer bearing ring to get to the spray oil hole and thus into the bearing interior.
  • the pressure of the oil at the spray oil holes and thus the amount of oil supplied to the bearing interior can be adjusted specifically.
  • the amount of oil is adjusted to allow for sufficient cooling and lubrication.
  • as little oil as possible should pass through the storage rows in order to keep the churning losses low.
  • the securing element used for fixing the holes to each other can be designed differently both in terms of its positioning and in terms of its shape.
  • the securing element may be formed as a pin, a pin or as a bolt.
  • the securing element is in this case attached to the bearing cartridge such that it is connected both to the carrier ring and to the outer bearing ring.
  • the use of a plurality of securing elements is conceivable, which serve the rotationally secure fixing of the outer bearing ring to the support ring and thus allow the targeted application of the bearing interior.
  • 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 housing is formed in particular with a receiving bore for the bearing, wherein the inner diameter of the receiving bore is slightly larger than the outer diameter of the outer bearing ring. The resulting in this case for the formation of the oil film gap, which is formed for example as a gap, is accordingly by the Dimensions of the mounting hole and the bearing cartridge or the outer bearing ring determined.
  • the support ring arranged within the bearing housing makes it possible to design the bearing cartridge flexibly in accordance with the respective requirements.
  • the bearing cartridge can be preassembled according to customer requirements by the bearing components are positioned within the carrier ring.
  • the storage cartridge can be delivered to the customer together with all provided storage components.
  • the vibration damping oil film is formed in the space between the support ring and the bearing housing.
  • a number of supply holes may be formed in the bearing housing, which are communicatively connected in the installed state with circumferential grooves surrounding the outer circumference of the bearing cartridge. In this way, oil from the engine oil circuit can be pressed into the gap and thus used to supply the Quetschölfilms. From the grooves in the bearing cartridge, a part of 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.
  • an outlet bore is preferably further provided in the bearing housing.
  • This outlet hole may communicate with drain groove formed on the outer circumference of the outer bearing ring, so that the oil supplied to the clearance through the supply hole can continuously flow away.
  • the bearing itself may be formed, for example, as a rolling bearing.
  • the bearing has an outer bearing ring.
  • the warehouse also includes if an inner bearing ring, wherein between the two bearing rings a number of rolling elements is performed.
  • the rolling elements are guided in WälzSystemterrorismbahnen, 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 manufactured either in one or two parts. In a two-part production of the outer bearing ring, for example, a spacing of the two partial rings by means of a prestressed spring element is conceivable.
  • the bearing rings are made in particular of temperature and corrosion resistant materials, such as hardened steels. Furthermore, it is also conceivable that the bearing has only one outer bearing ring and the function of the inner bearing ring is taken over by the shaft, in which case the WälzSystemterrorismen are introduced into the shaft and the rolling elements between the outer bearing ring and the shaft out.
  • the securing element additionally serves as a means for securing transport. Thanks to this additional function of the securing element can be dispensed with the use of separate transport safety devices. As a result, for example, the manufacturing costs and assembly costs of the bearing cartridge can be reduced. Furthermore, an assembly of the storage cartridge is made possible before delivery to the customer and facilitates the customer according to the installation of the storage cartridge.
  • the inner bearing ring itself serves as a transport lock when this is made in one piece and pressed onto the shaft.
  • a separate transport securing means which, for example, when using only one nes securing element takes over the function of the transport lock.
  • the securing element is positively connected to the carrier ring.
  • the securing element may in this case be designed, for example, as a pin which is connected in a form-fitting manner to the carrier ring and which extends radially inwards in the direction of the center axis of the bearing housing.
  • the bolt preferably engages in a groove which is formed on the outer circumference of the outer bearing ring.
  • the securing element is preferably connected to the bearing housing so that it is fixed to the housing.
  • the securing element may be formed, for example, as a housing-fixed profile, which extends in the installed state radially in the direction of the center axis of the bearing unit inwardly.
  • the securing element can preferably pass through a bore in the carrier ring, so that radially inwardly extending end of the securing element is connected to the outer bearing ring. and terminates between the axially spaced apart part rings of the outer race.
  • the securing element is designed as a socket.
  • the bush can be arranged, for example, fixed to the housing at the top of the bearing unit in the installed state of the bearing cartridge and thus serves in the assembled state of the bearing unit of the support of the support ring and the support of the outer bearing rings. In this way, after mounting the bearing cartridge, a twist is hen the bearing cartridge against the bearing housing prevented.
  • the securing element is designed as a transport lock for the bearing cartridge.
  • the securing element can be arranged, for example, as a bolt connected fixedly to the carrier ring from the upper side of the bearing unit.
  • the transport lock for the bearing cartridge is designed as a socket.
  • the bushing is in particular firmly connected to the carrier ring and in this way makes it possible to secure the outer bearing ring within the carrier ring.
  • the outer bearing ring is rotationally and axially secured relative to the carrier ring.
  • an axial displacement and / or rotation of the carrier ring during transport of the bearing cartridge is prevented.
  • the design of the securing element as a hollow and firmly connected to the support ring sleeve preferably also allows the oil drain through the interior of the socket.
  • the bearing unit can each comprise both a housing-fixed and a socket firmly connected to the support ring.
  • the carrier ring comprises an axial abutment surface for the outer bearing ring.
  • the securing element is designed as an axial stop for the outer bearing ring.
  • a securing element is included, which likewise serves as an axial stop for two partial rings of an outer bearing ring.
  • two securing elements can be included, which are each used as an axial stop for each part ring.
  • the bore in the support ring via a the outer bearing ring on its outer circumference circumferential groove communicating with the spray oil hole.
  • the oil flows from the hole in the carrier ring via the groove and the spray oil hole in the bearing interior or rotates the outer bearing ring first.
  • the outer race encircling groove is thus effectively formed as a supply groove for the spray oil hole and supports the metering of oil in the bearing interior.
  • a configuration is also possible in which the bore in the carrier ring is connected communicating with the spray oil bore via a groove running around the carrier ring on its inner circumference.
  • the carrier ring comprises a circumferential groove surrounding its outer circumference, which is connected to the supply bore in the bearing housing.
  • the groove connected to the supply bore in the bearing housing can in principle also be formed on the inner circumference of the bearing housing itself.
  • the outer bearing ring is designed in two parts, wherein the two partial rings are axially spaced from each other.
  • a spring element can be used, which presses the partial rings against the rolling elements and this in turn against the WälzSystemterrorism of the inner ring via its spring force.
  • the bearing housing comprises a front side phase for mounting the bearing cartridge.
  • the phase is preferably formed as a chamfer, which allows easy mounting of the storage unit.
  • FIG. 5 shows a further bearing unit for a turbocharger in a longitudinal section
  • FIG. 6 shows the bearing unit according to FIG. 5 in a further longitudinal section
  • FIG. 8 shows the bearing unit according to FIG. 7 in a further longitudinal section
  • FIG. 9 shows a further bearing unit for a turbocharger in a longitudinal section
  • FIG. 10 shows the bearing unit according to FIG. 9 in a further longitudinal section
  • FIG. 10 shows the bearing unit according to FIG. 9 in a further longitudinal section
  • FIG. 11 shows a further bearing unit for a turbocharger in a longitudinal section
  • FIG. 16 shows the bearing unit according to FIG. 15 in a cross section
  • 17 shows a further bearing unit for a turbocharger in a longitudinal section
  • FIG. 18 shows the bearing unit according to FIG. 17 in a cross section
  • FIG. 21 the snap element according to FIGS. 17 to 20 in a cross section.
  • FIG. 22 shows a further bearing unit for a turbocharger in a longitudinal section, Fig. 23, the bearing unit of FIG. 22 in a cross section, and
  • the following exemplary embodiments each show a bearing unit for a turbocharger in various sectional views.
  • An essential difference between the embodiments lies in the relative positioning of the spray oil holes in the outer bearing ring to the holes in the carrier ring.
  • the remaining bearing components have substantially the same nature and function, so that the detailed description of FIGS. 1 to 4 can be analogously transferred to the other embodiments of FIGS. 5 to 24.
  • the bearing unit 1 shows a bearing unit 1 for a turbocharger in a longitudinal section.
  • the bearing unit 1 comprises a bearing cartridge 3, which is arranged in an axially extending metallic bearing housing 5.
  • a bearing 7 designed as a double-row angular contact ball bearing is positioned in this bearing.
  • the bearing 7 is formed with an outer bearing ring 9 and with an inner bearing ring 1.
  • Both bearing rings 9, 1 1 are made in two parts and each consist of two partial rings 13, 15, 17, 19.
  • the partial rings 17, 19 of the inner bearing ring 1 1 are arranged on a shaft 21.
  • As rolling elements 23 1 1 balls are inserted between the bearing rings.
  • the bearing 7 is arranged within a carrier ring 25.
  • the partial rings 13, 15 of the outer bearing ring 9 are spaced apart axially by a spring element 27.
  • the spring element 27 presses part rings 13, 15 axially outward against the rolling elements 23.
  • the Spring element 27 ensures that the partial rings 13, 15 of the outer bearing ring 9 are pressed with the spring force against the rolling elements 23 and these in turn are pressed against the WälzEffbahn on the inner circumference of the partial rings 17, 19 of the inner bearing ring 11.
  • a gap 29 in the form of a gap with a vibration-damping oil film 31 is formed.
  • the oil film 31 is supplied in the installed state via two supply holes 33, 35 in the bearing housing 5 with oil.
  • the supply holes 33, 35 are each connected to grooves 37, 39 which rotate around the support ring 25 on its outer periphery.
  • the grooves 37, 39 are connected to the bores 41, 43, via which in each case grooves 45, 47 are acted upon in the partial rings 13, 15 with oil.
  • the holes 41, 43 are not visible due to the representation in Fig. 1, but can be seen in FIG. 3.
  • the oil, which enters the grooves 45, 47, is metered from there via injection oil bores 49, 51 into the bearing interior 53.
  • the bearing 7 is supplied with oil and allows lubrication of the individual bearing components.
  • a small amount of the oil from the respective grooves 45, 47 escape through the gap between the partial rings 13, 15 of the outer bearing ring 9 and the support ring 25.
  • the bearing cartridge 3 has two positively connected to the support ring bolts 55, 57.
  • the bolts 55, 57 are aligned vertically to the bearing housing axis. They extend from the bearing housing 5, starting radially inward in the direction of the shaft 21st
  • the bolts 55, 57 each engage in a groove 59, 61 in the outer periphery of the partial rings 13, 15 of the outer bearing ring 9, so that the partial rings 13, 15 can not rotate relative to the support ring 25.
  • the bolts 55, 57 serve to transport the bearing cartridge 3, i. before pressing this on the shaft 21, as a transport lock. This configuration enables a simplified assembly of the storage unit 1 and a simple transport to the customer.
  • a locking element designed as a securing pin 63 is arranged on the end face of the bearing cartridge 3, which engages in a bore 65 in the bearing housing 5.
  • the securing element 63 serves to prevent rotation of the bearing cartridge 3 relative to the bearing housing 5 and can be seen in FIGS. 3 and 4.
  • the support ring 25 is provided at its outer periphery with a drain groove 67.
  • the drainage groove 67 is communicatively connected to an outlet bore 69 in the installed state of the bearing 7.
  • the oil also flows in the axial direction outside between the support ring 25 and the bearing housing 5.
  • the bearing housing 5 is frontally formed with a phase 70.
  • the phase 70 is formed as a chamfer, which facilitates the mounting of the individual bearing components.
  • the carrier ring 25 is formed with two axial abutment surfaces 71, 73 for the partial rings 13, 15 of the outer bearing ring 9. In this way, a displacement of the partial rings 13, 15 is prevented in the axial direction and enables a secure positioning of the individual bearing components in the operation of the turbocharger and during the movement of the while 21.
  • FIG. 3 shows the bearing unit according to FIGS. 1 and 2 in a further longitudinal section. This section allows the exact representation of the arrangement of the spray oil holes 49, 51 in the sub-rings 13, 15 of the outer bearing ring 9 relative to the holes 4, 43 in the support ring 25th
  • Both the holes 41, 43 in the carrier ring 25 and the spray oil holes 49, 51 are formed on the underside of the bearing unit 1.
  • the metered via the supply holes 33, 35 from the top of the storage unit 1 oil is passed through the formed in the outer periphery of the carrier ring 25 grooves 37, 39 to the underside of the carrier ring 25 and from there via the holes 41, 43 into which the partial rings 13th , 15 of the outer race 9 dosed on the outer circumference circumferential grooves 45,47.
  • the spray oil holes 49, 51 are supplied with oil, which is then fed to the bearing interior 53 and used there for lubrication of the bearing components.
  • the securing pin 63 can be seen in the bore 65 on the end face of the bearing housing 5.
  • the securing pin 63 serves to prevent rotation of the carrier ring 25 and partial rings 13, 15 to the bearing housing 5.
  • the bearing unit according to FIGS. 1 to 3 seen in a further cross-section. On the basis of this illustration, one can clearly see the securing pin 63, which serves as a means of preventing the rotation of the components of the bearing cartridge 3 relative to the bearing housing 5.
  • the security against rotation is achieved here by a form fit during the installation of a flattening of the securing pin 63 on a counterflattening of the bearing housing 5.
  • abutment of the respective flattenings to one another results in a holding force by positive engagement in the plant edge area between the flats of the securing pin 63 and the counterflattening of the bearing housing.
  • the bearing unit 81 comprises the axially extending metallic bearing housing 5 arranged bearing cartridge 3 and designed as a double-row angular contact ball bearing 7 with an outer bearing ring 9 and an inner bearing ring 1 1.
  • Both bearing rings 9, 1 1 are made in two parts and each consist of two Part rings 13, 15, 17, 19.
  • bearing unit 81 Since the bearing unit 81 has substantially the same bearing components as the bearing unit 1 already described, reference is made at this point to the comprehensive description there.
  • the difference from the above-described bearing unit 1 consists in the positioning of the bore 41, 43 in the carrier ring 25 and the spray oil holes 49, 51 in the partial rings 13, 15 of the outer bearing ring 9.
  • the holes 41, 43, 49, 51 formed at the top of the storage unit.
  • the pressure loss of the oil is particularly low.
  • the coming of the supply holes 33, 35 coming Oil can essentially in a direct way, so without the support ring 25 in the grooves 37, 39 to circulate on the circumference, pass through the holes 41, 43 in the grooves 45, 47 in the outer periphery of the partial rings 13, 15 and from there into the spray oil holes 49, 51 are metered.
  • bolts 55, 57 are also aligned vertically to the bearing housing axis and extend from the bearing housing 5, starting radially inward in direction the shaft 21. To prevent twisting, they each engage in a groove 59, 61 in the outer periphery of the partial rings 13, 15 a. Furthermore, the bolts 55, 57 during transport of the bearing cartridge 3, so before pressing this on the shaft 21, as a transport lock.
  • FIG. 6 shows the bearing unit 81 according to FIG. 5 in a further longitudinal section. This illustration clearly shows the securing pin 63.
  • the latter engages in the bore 65 in the bearing housing 5 and serves to prevent rotation of the components of the bearing cartridge 3 with respect to the bearing housing 5, wherein the anti-rotation lock by a positive connection in the plant of a flattening of the securing pin 63rd is achieved at a Gegenabflachung of the bearing housing 5.
  • FIG. 7 shows a further bearing unit 101 for a turbocharger in a longitudinal section.
  • the bearing unit 101 also comprises the bearing cartridge 3 arranged in the axially extending metallic bearing housing 5 and a bearing 7 designed as a double-row angular contact ball bearing with an outer bearing ring 9 and with an inner bearing ring 1.
  • both bearing rings 9, 11 are made in two parts and each consist of two parts rings 13, 15, 17, 19. Reference is made to FIGS. 1 to 4 for further description.
  • the bores 41, 43 in the carrier ring 25 are formed on the upper side of the bearing unit 101 and the spray oil bores 49, 51 in the partial rings 13, 15 of the outer bearing ring 9 on the underside of the bearing unit 101.
  • the oil metered by the supply bores 33, 35 via the bores 4, 43 into the grooves 45, 47 circulates the partial rings 13, 15 along half the circumference and is then metered into the bearing interior 53 via the fuel oil bores 49, 51.
  • FIG. 8 shows the bearing unit 101 according to FIG. 7 in a further longitudinal section.
  • the securing pin 63 which engages against rotation on the end face of the bearing cartridge 3 in the bore 65 in the bearing housing 5.
  • the axial abutment surfaces 71, 73 on the support ring 25 can be clearly seen here.
  • the axial abutment surfaces 71, 73 allow a secure positioning of the partial rings 13, 15 of the outer bearing ring 9 even during the axial movement of the shaft 21st
  • FIG. 9 shows a further bearing unit 121 for a turbocharger in a longitudinal section.
  • the bearing unit 101 comprises the bearing cartridge 3, which is arranged in the axially extending metallic bearing housing 5. Furthermore, the bearing unit 101 comprises a designed as a double-row angular contact ball bearing 7 with an outer bearing ring 9 and with an inner bearing ring 1 1, both in two parts, each with two partial rings 13, 15, 17,19 are made.
  • the detailed description of these and the other bearing components can, as already mentioned, be taken from the above-described figures.
  • the arrangement of the spray oil holes 49, 51 in the sub-rings 13, 15 of the outer bearing ring 9 relative to the holes 41, 43 in the support ring 25 according to the present bearing unit 121 corresponds to the arrangement of the bearing unit 1 according to FIGS.
  • the difference of the bearing unit 121 to the storage unit 1 is in the additional function of the trained as a bolt 55, 57 fuse elements.
  • the bolts 55, 57 serve to secure the outer bearing ring 9 or its partial rings 13, 15 within the carrier ring 25 in a manner secure against rotation. This ensures the uniform and targeted supply of oil to the bearing interior space.
  • the bolts 55, 57 also serve as an axial stop for the partial rings 13, 15 of the outer bearing ring.
  • the axial stop is thus not provided by the carrier ring 25, but by the fuse element. Accordingly, the bolts 55, 57 prevent axial displacement of the partial rings 13, 15 along the shaft 21.
  • the bolts 55, 57 serve to transport the bearing cartridge 3, ie, before it is pressed onto the shaft 21, as a transport lock.
  • FIG. 10 shows the bearing unit 121 according to FIG. 9 in a further longitudinal section. Based on this illustration, the arrangement of the holes 41, 43, 49, 51 can be seen each other.
  • Both the holes 41, 43 in the support ring 25 and the spray oil holes 49, 51 are formed on the underside of the bearing unit 1, so that the metered from the top oil is on the formed in the outer periphery of the support ring 25 grooves 37, 39 to the underside of Carrier ring 25 is passed.
  • the spray oil holes 49, 51 are supplied with oil, which is then fed to the bearing interior 53 and used there to lubricate the bearing components.
  • the required amount of oil for bearing lubrication can also be set by means of the targeted positioning of the holes 41, 43, 49, 51 relative to one another.
  • FIG. 11 also shows a further bearing unit 141 for a turbocharger in a longitudinal section.
  • the bearing unit 141 comprises the bearing cartridge 3 arranged in the axially extending metallic bearing housing 5 and a bearing 7 designed as a double-row angular contact ball bearing with an outer bearing ring 9 and with an inner bearing ring 11.
  • the outer bearing ring is made in two parts from two partial rings 13, 15, whereas the inner bearing ring 1 1 is made in one piece.
  • the arrangement of the spray oil holes 49, 51 in the sub-rings 13, 15 of the outer bearing ring 9 relative to the holes 41, 43 in the support ring 25 corresponds to the arrangement of the bearing unit 1 and the bearing unit 121st
  • the difference between the bearing unit 141 and the bearing unit 1 is that in the present case only one locking element configured as a bolt 57 is connected in a form-locking manner with the support ring 25 to prevent rotation.
  • the bolt 57 serves as rotation of the partial ring 15 outer bearing ring 9 relative to the support ring 25.
  • the axial stop of the partial ring 15 is taken over by the bolt.
  • the partial ring 13 of the outer bearing ring 9 is in contrast to the previous bearing units taken over by the securing pin 63, which engages on the end face of the bearing cartridge 3 in the bore 65 in the bearing housing 5.
  • FIG. 12 the bearing unit according to FIG. 1 1 is shown in a further longitudinal section. All holes 41, 43, 49, 51 are formed on the underside of the bearing unit 141, so that the oil supply of the bearing interior 53 is carried out accordingly from the bottom.
  • FIG. 13 shows a further bearing unit 161 for a turbocharger in a longitudinal section.
  • the bearing unit 101 comprises the bearing cartridge 3, which is arranged in the axially extending metallic bearing housing 5. Furthermore, the bearing unit 101 comprises a bearing 7 designed as a double-row angular contact ball bearing with an outer bearing ring 9.
  • this bearing unit 161 is formed with the roller body raceways for guiding the rolling elements 23.
  • the use of separately mounted inner bearing rings 1 1, or partial rings 17, 19 can be dispensed with entirely.
  • the shaft 21 thus assumes even the function of the partial rings 17, 19, so that a safe mounting of the shaft 21 can be achieved in a turbocharger by such a configuration with low cost and assembly costs.
  • dispensing with a separate inner bearing rings 1 1 or partial rings 17, 19 the sum of the component tolerances can be reduced.
  • the usually adding shape and position errors of the partial rings 17, 19 on the shaft 21 can thus be avoided, as a result of which the tolerance is lower overall.
  • the spray oil holes 49, 51 in the sub-rings 13, 15 of the outer bearing ring 9 relative to the holes 41, 43 in the support ring 25 are also here the underside of the bearing unit 161 arranged so that the oil supply to the bearing interior 53 takes place from below.
  • FIG. 14 shows the bearing unit 161 according to FIG. 13 in a further longitudinal section. Based on this section, the relative positioning of the bores 41, 43 in the carrier ring 25 to the spray oil holes 49, 51 is shown. The oil supply via the supply bores 33, 35 takes place from the upper side of the storage unit 161, whereas the supply of the storage trough space 53 takes place from the underside.
  • the anti-rotation of the partial ring 13 by the securing pin 63 can be seen on the basis of the sectional view. Instead of a second bolt, the rotation is taken over here by the recorded in the bore 65 of the bearing housing 5 locking pin 63.
  • FIG. 15 shows a further bearing unit 181 for a turbocharger in a longitudinal section.
  • the bearing unit 181 comprises the bearing in the axially extending metallic bearing housing 5 bearing cartridge 3 and designed as a double-row angular contact ball bearing 7 with an outer bearing ring 9 and an inner bearing ring 1 1.
  • the outer bearing ring is present in two parts of two sub-rings 13, 15 made , the inner bearing ring 11 is made in one piece.
  • the bearing unit 181 has both the holes 41, 43 in the carrier ring 25 and the spray oil holes 49, 51 on the underside of the storage unit 181 on. Due to the illustration, however, the holes 41, 43, 49, 51 are not shown here.
  • the oil application of the bearing components of the bearing 7 takes place from the underside of the bearing cartridge 3.
  • a securing element formed as a housing-fixed profile 75 is used.
  • the housing-fixed profile 75 extends radially in the direction of the shaft 21 inwardly through a groove 76 in the support ring 25 therethrough.
  • it fulfills the function of preventing rotation of the partial rings 13, 15 of the outer bearing ring 9 relative to the carrier ring 25 and also secures the bearing cartridge 3 against rotation relative to the bearing housing 5.
  • the use of a separate securing pin on the front side of the bearing housing 5, as this can be seen for example in the storage unit 1 according to FIGS. 1 to 4, can be omitted here.
  • the axial abutment of the partial rings 13, 15 of the outer bearing ring 9 with respect to the bearing housing 5 is achieved via a positive connection of the engaging profile 75.
  • the transport safety of the bearing cartridge 3 is ensured via the one-piece inner bearing ring 1 1.
  • FIG. 16 shows the bearing unit according to FIG. 15 in a cross section. Based on this representation, the housing-fixed profile 75 is clearly visible. The profile extends through the groove 76 in the carrier ring 25 and ends between the partial rings 13, 15 of the outer bearing ring 9.
  • the profile 75 serves both the rotation of the partial rings 13, 15 to the support ring 25, as well as the rotation of the bearing cartridge 3 to the bearing housing 5.
  • a locking pin can be omitted in this embodiment.
  • FIG. 17 also shows a further bearing unit 201 for a turbocharger in a a longitudinal section.
  • the bearing unit 201 has an axially extending metallic bearing housing 5 with a bearing cartridge 3 arranged therein and a bearing 7 designed as a double-row angular contact ball bearing with an outer bearing ring 9 and with an inner bearing ring 11.
  • both bearing rings 9, 1 1 are made in two parts and each consist of two partial rings 13, 15, 17, 19.
  • Both the holes 41, 43 in the support ring 25 and the spray oil holes 49, 51 are formed on the underside of the bearing unit 181, so that the oil is applied to the bearing components of the bearing 7 from the bottom of the bearing cartridge 3.
  • the bearing unit 201 likewise has a securing element embodied as a housing-fixed profile 75, which extends radially inwardly in the direction of the shaft 21 through the groove 76 in the carrier ring 25.
  • the profile 75 fulfills the function of preventing rotation of the partial rings 13, 15 of the outer bearing ring 9 relative to the support ring 25 and additionally the bearing cartridge 3 relative to the bearing housing 5.
  • the axial stop of the partial rings 13, 15 of the outer bearing ring 9 relative to the bearing geregehoffkla 5 reaches over a positive connection of the engaging profile 75. Again, can be dispensed with the use of a separate security pins to prevent rotation of the bearing cartridge 3
  • a snap element 77 is used to secure the transport.
  • the snap element 77 connects both partial rings 17, 19 of the two-piece bearing ring 11 with each other and thus prevents slippage and tilting of the bearing components to each other. Accordingly, thanks to the snap element 77, a transport of the preassembled storage unit 201 to the customer is possible.
  • FIG. 18 shows the bearing unit according to FIG. 17 in a cross section. Based on this representation, the housing-fixed profile 75 is clearly visible. The profile extends through the groove 76 in the carrier ring 25 and ends between see the partial rings 13, 15 of the outer bearing ring 9. Furthermore, the substantially circular snap element 77 can be seen, which connects the partial rings 17, 19 of the inner bearing ring 1 1 together. 19 shows the bearing unit 201 according to FIGS. 17 and 18 in a further longitudinal section. Also with reference to this illustration, the positioning of the snap element 77 can be clearly seen.
  • both the holes 41, 43 in the support ring 25 and the spray oil holes 49, 51 in the sub-rings 13, 15 of the outer bearing ring 9 are formed on the underside of the bearing unit 1, so that the metered from the top oil is on the outer circumference of the support ring 25 formed grooves 37, 39 is passed to the underside of the carrier ring 25.
  • the spray oil holes 49, 51 are supplied with oil, which is then metered into the bearing interior 53.
  • the snap element 77 according to FIGS. 17 to 19 is shown as a separate component. It can be seen both the substantially circular shape and the snap lugs, which connect the partial rings 17, 19 of the inner bearing ring 1 1 together.
  • the snap element 77 can be positioned during assembly between the partial rings 17, 19 and prevented by snapping their slippage or an axial displacement.
  • FIG. 22 shows a further bearing unit 221 for a turbocharger in a longitudinal section.
  • the bearing unit 221 also comprises the bearing cartridge 3 arranged in the axially extending metallic bearing housing 5 and a bearing 7 designed as a double-row angular contact ball bearing with an outer bearing ring 9 and with an inner bearing ring 11.
  • ring is made in two parts of two partial rings 13, 15, whereas the inner bearing ring 1 1 is made in one piece.
  • the oil supply of the bearing unit 221 takes place here from the top.
  • the holes 41, 43 in the support ring 25 and the spray oil holes 49, 51 are formed on the top.
  • the oil metered in via the supply bores 33, 35 neither has to circulate the carrier ring 25 nor the partial rings 13, 15 of the outer bearing ring 9, but can be metered directly into the spray oil bores by the grooves 45, 47 in the partial rings 13, 15.
  • a housing-fixed bushing 78 is inserted as a securing element on the top side of the bearing unit 221, which engages through a bore 79 in the carrier ring 25 so that the radially inwardly extending end of the bushing 78 between the axially spaced-apart partial rings 13, 15 of outer bearing ring 9 ends.
  • the bushing 78 secures the bearing cartridge 3 and thus serves in the assembled state of the bearing unit 221 of the rotational and axial support of the carrier ring 25. In this way, the secure positioning of the bearing cartridge 3 in the bearing housing 5 can be made possible in the mounted state.
  • a further bushing 80 is arranged on the underside of the bearing unit 221.
  • the sleeve 80 is fixedly connected to the carrier ring 25 and serves fulfilled in two respects the function as a fuse element.
  • a rotational and axial securing of the partial rings 13, 15 of the outer bearing ring 9 relative to the carrier ring 25 is made possible by the sleeve 80.
  • axial movement and rotation of the carrier ring 25 during transport of the bearing cartridge 3 are prevented by means of the bush 80.
  • the carrier ring 25 is supported in the operation of the turbocharger against the bushing 78, the partial rings 13, 15 of the outer bearing ring 9 are both supported against the sleeve 78 as well as the sleeve 80.
  • both bushes 78, 80 prevents both a rotation of the partial rings 13, 15 of the inner bearing ring 9 relative to the support ring 25 and a rotation of the bearing cartridge 3 relative to the bearing housing 5.
  • the relative positioning of the holes 41, 43 in the support ring 25 to the Spray oil holes in the partial rings 13, 15 is therefore fixed.
  • the drainage of the oil from the intermediate space 29 can also take place through the interior of the bushing 80.
  • FIG. 23 shows the bearing unit 221 according to FIG. 22 in a cross section.
  • the bushing 78 which engages through the bore 79 in the carrier ring 25. It ends between the partial rings 13, 15 and serves equally as anti-rotation and as an axial stop.
  • both a transport securing of the partial rings 13, 15 of the outer bearing ring 9 within the carrier ring 25 can be achieved, as can the anti-twist protection of the bearing cartridge 3 are ensured within the bearing housing 5.
  • FIG. 24 shows the bearing unit 221 according to FIGS. 22 and 23 in a further longitudinal section. Due to the one-piece design of the inner bearing ring serves as a transport of the partial rings 13, 15 of the outer bearing ring 9. So can be dispensed with the use of separate transport locks at this point, which, for example, manufacturing costs and Montageauf - Wall of the bearing cartridge 3 can be reduced. Furthermore, an assembly of the storage cartridge is made possible before delivery to the customer and facilitates the customer according to the installation of the storage cartridge.
  • the relative positioning of the spray oil holes 49, 51 in the outer bearing ring 9 and in the sub-rings 13, 15 of the outer bearing ring 9 to the holes 41, 43 in the support ring 25 is not limited to the presented embodiments.
  • the respective bores 41, 43, 49, 51 can be introduced according to the requirements of a bearing unit at arbitrary locations along the circumference of the carrier ring 25 or of the outer bearing ring 9.
  • the shape or the cross section of the respective bores 41, 43, 49, 51 may in this case vary, in particular by the vote he cross sections of the holes 41, 43 in the support ring 25 and the spray oil holes 49, 51 implement the targeted metering of oil.
  • the amount of oil metered into the bearing trough space 53 can be adjusted by tuning the bores 41, 43, 49, 51 in such a way that sufficient cooling and lubrication are made possible. On the other hand, as little oil as possible should pass through the rows of warehouses in order to keep the churning losses low.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Acoustics & Sound (AREA)
  • Aviation & Aerospace Engineering (AREA)
  • Supercharger (AREA)
  • Rolling Contact Bearings (AREA)

Abstract

L'invention porte sur une unité de palier (1, 81, 101, 121, 141, 161, 181, 201, 221) pour un turbocompresseur, comprenant un boîtier de palier (5) s'étendant dans une direction axiale, une cartouche de palier (3) disposée à l'intérieur du boîtier de palier (5) et possédant une bague porteuse (25), ainsi qu'un palier (7) positionné dans cette cartouche et comprenant une bague de palier extérieure (9, 13, 15), un espace intermédiaire (29) pour un film d'huile (31) servant à amortir les vibrations étant formé entre le boîtier de palier (5) et la cartouche de palier (3), la bague porteuse (25) présentant un perçage (41, 43) qui est en communication avec un perçage d'huile de pulvérisation (49, 51) destiné à la lubrification du palier qui est formé dans une bague extérieure de palier (9, 13, 15). La position de la bague extérieure de palier (9, 13, 15) et la position du perçage d'huile de pulvérisation (49, 51) sont fixées de façon bloquée en rotation relative par rapport au perçage (41, 44) de la bague porteuse (25) au moyen d'un élément d'arrêt (55, 57, 63, 75, 78, 80). Cette fixation garantit une alimentation en huile adéquate de la cavité intérieure (53) du palier.
PCT/EP2011/065895 2010-12-17 2011-09-14 Unité de palier pour turbocompresseur WO2012079788A1 (fr)

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DE102010054996A DE102010054996A1 (de) 2010-12-17 2010-12-17 Lagereinheit für einen Turbolader
DE102010054996.7 2010-12-17

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Cited By (4)

* Cited by examiner, † Cited by third party
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EP2722494A1 (fr) * 2012-10-19 2014-04-23 Aktiebolaget SKF Turbocompresseur, en particulier pour un moteur à combustion et procédé de fabrication d'un tel turbocompresseur
DE102013004499A1 (de) * 2013-03-14 2014-09-18 Minebea Co., Ltd. Lagersystem
US20150078696A1 (en) * 2012-04-20 2015-03-19 Schaeffler Technologies Gmbh & Co. Kg Bearing unit for a turbocharger
WO2016102049A1 (fr) * 2014-12-22 2016-06-30 Ihi Charging Systems International Gmbh Dispositif de palier pour un turbocompresseur à gaz d'échappement et turbocompresseur à gaz d'échappement

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DE102014212145B4 (de) * 2014-06-25 2021-11-11 Vitesco Technologies GmbH Turbolader und Montageverfahren für einen Turbolader
DE102015213176A1 (de) * 2015-07-14 2017-01-19 Continental Automotive Gmbh Lageranordnung für eine Welle
DE102016209149A1 (de) 2016-01-22 2017-07-27 Minebea Co., Ltd. Lagereinheit für einen Abgasturbolader oder eine Abgasnutzturbine und Lagerung mit einer solchen Lagereinheit
DE102018202301A1 (de) 2018-02-15 2019-08-22 Minebea Mitsumi Inc. Lagereinheit für einen Turbolader oder eine Abgasnutzturbine, sowie Turbolader und Abgasnutzturbine mit einer solchen Lagereinheit
DE102018008749A1 (de) 2018-11-07 2020-05-07 Daimler Ag Lagervorrichtung für eine Welle eines Turboladers
CN110905919A (zh) * 2019-12-23 2020-03-24 至玥腾风科技集团有限公司 一种并联轴承

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US5253985A (en) * 1990-07-04 1993-10-19 Mtu Motoren- Und Turbinen-Union Friedrichshafen Gmbh Exhaust gas turbocharger having rotor runners disposed in roller bearings
DE69012346T2 (de) 1989-12-12 1995-03-16 Allied Signal Inc Axiale lagerhalterung mit schmierstoffzuführung für einen turbolader.
EP1705393A1 (fr) * 2003-12-10 2006-09-27 Jtekt Corporation Dispositif de palier pour turbocompresseur

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DE69012346T2 (de) 1989-12-12 1995-03-16 Allied Signal Inc Axiale lagerhalterung mit schmierstoffzuführung für einen turbolader.
US5253985A (en) * 1990-07-04 1993-10-19 Mtu Motoren- Und Turbinen-Union Friedrichshafen Gmbh Exhaust gas turbocharger having rotor runners disposed in roller bearings
EP1705393A1 (fr) * 2003-12-10 2006-09-27 Jtekt Corporation Dispositif de palier pour turbocompresseur

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20150078696A1 (en) * 2012-04-20 2015-03-19 Schaeffler Technologies Gmbh & Co. Kg Bearing unit for a turbocharger
US9212698B2 (en) * 2012-04-20 2015-12-15 Schaeffler Technologies AG & Co. KG Bearing unit for a turbocharger
EP2722494A1 (fr) * 2012-10-19 2014-04-23 Aktiebolaget SKF Turbocompresseur, en particulier pour un moteur à combustion et procédé de fabrication d'un tel turbocompresseur
DE102013004499A1 (de) * 2013-03-14 2014-09-18 Minebea Co., Ltd. Lagersystem
WO2016102049A1 (fr) * 2014-12-22 2016-06-30 Ihi Charging Systems International Gmbh Dispositif de palier pour un turbocompresseur à gaz d'échappement et turbocompresseur à gaz d'échappement

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