WO2024104529A1 - Palier axial pour supporter un arbre rotatif et turbocompresseur à gaz d'échappement possédant un palier axial - Google Patents

Palier axial pour supporter un arbre rotatif et turbocompresseur à gaz d'échappement possédant un palier axial Download PDF

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Publication number
WO2024104529A1
WO2024104529A1 PCT/DE2023/100830 DE2023100830W WO2024104529A1 WO 2024104529 A1 WO2024104529 A1 WO 2024104529A1 DE 2023100830 W DE2023100830 W DE 2023100830W WO 2024104529 A1 WO2024104529 A1 WO 2024104529A1
Authority
WO
WIPO (PCT)
Prior art keywords
groove
section
axial bearing
lubricant
bearing
Prior art date
Application number
PCT/DE2023/100830
Other languages
German (de)
English (en)
Inventor
Henryk JOHN
Matthias DEUTSCHER
Alessandro CICOLIN
Sotirios NIKOLAIDIS
Sven Becker
Dominic König
Roberto De Santis
Original Assignee
Ihi Charging Systems International Gmbh
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 Ihi Charging Systems International Gmbh filed Critical Ihi Charging Systems International Gmbh
Publication of WO2024104529A1 publication Critical patent/WO2024104529A1/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
    • F16C17/00—Sliding-contact bearings for exclusively rotary movement
    • F16C17/04—Sliding-contact bearings for exclusively rotary movement for axial load only
    • F16C17/047—Sliding-contact bearings for exclusively rotary movement for axial load only with fixed wedges to generate hydrodynamic 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
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/02—Parts of sliding-contact bearings
    • F16C33/04—Brasses; Bushes; Linings
    • F16C33/06—Sliding surface mainly made of metal
    • F16C33/10—Construction relative to lubrication
    • F16C33/1025—Construction relative to lubrication with liquid, e.g. oil, as lubricant
    • F16C33/1045—Details of supply of the liquid to 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
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/02—Parts of sliding-contact bearings
    • F16C33/04—Brasses; Bushes; Linings
    • F16C33/06—Sliding surface mainly made of metal
    • F16C33/10—Construction relative to lubrication
    • F16C33/1025—Construction relative to lubrication with liquid, e.g. oil, as lubricant
    • F16C33/106—Details of distribution or circulation inside the bearings, e.g. details of the bearing surfaces to affect flow or pressure of the liquid
    • F16C33/1065—Grooves on a bearing surface for distributing or collecting the liquid
    • 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
    • F16C33/02—Parts of sliding-contact bearings
    • F16C33/04—Brasses; Bushes; Linings
    • F16C33/06—Sliding surface mainly made of metal
    • F16C33/10—Construction relative to lubrication
    • F16C33/1025—Construction relative to lubrication with liquid, e.g. oil, as lubricant
    • F16C33/106—Details of distribution or circulation inside the bearings, e.g. details of the bearing surfaces to affect flow or pressure of the liquid
    • F16C33/1075—Wedges, e.g. ramps or lobes, for generating 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
    • F16C2360/00—Engines or pumps
    • F16C2360/23—Gas turbine engines
    • F16C2360/24—Turbochargers

Definitions

  • Axial bearing for supporting a rotating shaft and exhaust gas turbocharger with an axial bearing
  • the invention relates to an axial bearing for supporting a rotatable shaft of the type specified in the preamble of patent claim 1. Furthermore, the invention relates to an exhaust gas turbocharger of the type specified in the preamble of patent claim 12.
  • Axial bearings in particular axial bearings for rotating shafts of exhaust gas turbochargers, are well known. They can be axial bearings in the form of a separate disk or axial bearings integrated in a sleeve, whereby a combination with radial bearings is possible. However, the invention relates to an axial bearing in the form of a sleeve.
  • a bearing bush is known from the published patent application DE 1 400 440 A, wherein the bearing bush has longitudinal grooves on its inner surface extending in the direction of a longitudinal axis for guiding lubricant. Radial grooves extending in the radial direction are formed on one end face of the bearing bush, wherein the longitudinal grooves and the radial grooves are arranged at a distance from one another.
  • the published patent application DE 11 2017 004 889 T5 discloses a bearing sleeve for an exhaust gas turbocharger, wherein longitudinal grooves extending in the direction of a longitudinal axis are formed on an inner surface of the bearing sleeve in each end section of the bearing sleeve, which grooves open into a radially extending radial groove on the respective end face of the bearing sleeve.
  • the radial groove is formed to extend only partially over the end face in the radial direction.
  • the published patent application WO 99/07982 A1 discloses a bearing sleeve for an exhaust gas turbocharger, wherein longitudinal grooves extending in the direction of a longitudinal axis are formed on an inner surface of the bearing sleeve, each of which opens into a radial groove formed on an end face.
  • the radial groove extends in the radial direction completely over an end face of the end face.
  • the invention is based on the object of specifying an axial bearing for a rotatable shaft which, in addition to improved running properties, has a higher load-bearing capacity and at the same time improved wear properties.
  • An axial bearing according to the invention for supporting a rotatable shaft has a first bearing body that is firmly connected to a bearing section of an exhaust gas turbocharger and a second bearing body that rotates with the shaft, wherein at least the first bearing body has a first sliding surface with an annular surface and with a surface profile.
  • a lubricating gap with lubricant is formed between the first sliding surface and a second sliding surface of the second bearing body.
  • a lubricant channel with a channel inlet and a channel outlet for supplying lubricant to the annular surface is formed in the first bearing body.
  • the first sliding surface is formed on an end face of a sleeve. It has at least one wedge surface and one locking surface, wherein the wedge surface is inclined starting from the locking surface.
  • the first sliding surface has a particle groove formed between the wedge surface and the locking surface, with a first groove end and a second groove end facing away from the first groove end, wherein the channel outlet is designed to receive the first groove end, and wherein the second groove end is formed in the radial direction at least on an outer edge of the annular surface or beyond, and wherein a first groove cross-section of the first groove end is larger or smaller than a second groove cross-section of the second groove end, and/or the particle groove has a round cross-section and the lubricant channel has a triangular or elliptical cross-section.
  • the advantage of the particle groove is that particles present in the lubricant are removed from the lubrication gap in a defined manner, thus reducing wear on the axial bearing. Furthermore, lubricant flow can be increased, which can result in improved cooling of the axial bearing and lower temperatures of a lubricant film, which can result in a greater lubricant thickness.
  • a greater lubricant thickness means a higher load-bearing capacity, which means that the axial bearing can be loaded with more force, thus increasing safety against failure.
  • the advantage of the lubricant channel with a triangular cross-section is that with the help of appropriately designed side ratios of the cross-section, with a constant groove width, different sized cross-sections can be realized in the lubricant channel, which have different particle size capacities. For example, if the groove depth of the groove essentially corresponds to the groove width, significantly larger particles can be accommodated in the groove than with a smaller groove depth with the same groove width.
  • the lubricant channel could also have an elliptical shape to achieve an appropriate absorption capacity for larger particles.
  • a virtual form line must of course be formed, since a groove by definition has an “open” side, which is described with the help of the virtual form line.
  • a first groove cross-section of the first groove end corresponds to a cross-section of the channel outlet.
  • a groove cross-section of the particle groove corresponds to a cross-section of the channel outlet.
  • a further simplified manufacture of the axial bearing according to the invention can be achieved if the particle groove is designed to extend in a straight line in the radial direction. Furthermore, particles can be absorbed and passed on more effectively than with a curved particle groove.
  • the axial bearing according to the invention can be further manufactured cost-effectively if the lubricant channel is designed to extend in the longitudinal direction of the sleeve.
  • a conical design of the particle groove makes it possible to achieve a better pressure distribution at the inlets and outlets of the particle groove in the lubricant flow so that the axial bearing can be optimally supplied with lubricant.
  • the particle groove has an oval or elliptical cross-section. The shape of the particle groove is thus designed for cost-effective production.
  • the second groove end has a second groove cross-section with a value of zero.
  • the lubricant channel has a non-circular, asymmetrical and/or freely formed channel outlet, with a surface transition from the channel outlet to the first sliding surface being elastohydrodynamically improved.
  • the first sliding surface has at least partially a microstructure, in particular in the area of at least one wedge surface and/or locking surface, which has a flow-directing and microdynamic effect on a lubricating medium.
  • the microstructure results in a flow-directing and microdynamic effect on the lubricant, whereby a more stable lubricating film can be brought about and thus the load-bearing capacity of the axial bearing can be increased, which ultimately further significantly improves the running properties of the axial bearing and further reduces the wear of the axial bearing.
  • the sliding and/or bearing surface has at least partially a friction and/or wear-reducing surface coating, which, for example, based on a carbon coating. This results in further improved running properties and a further reduction in wear of the axial bearing.
  • a further aspect of the invention relates to an exhaust gas turbocharger with a housing and a rotor, in particular comprising a compressor wheel and a turbine wheel connected in a rotationally fixed manner by means of a shaft, wherein according to the invention the housing has an axial bearing for supporting a shaft of the rotor, which is designed according to one of the previously described embodiments.
  • Fig. 1 shows a perspective view of a section of an exhaust gas turbocharger according to the invention with an axial bearing according to the invention in a first embodiment
  • Fig. 2 shows a side view of the bearing surface of the axial bearing according to the invention as shown in Fig. 1,
  • FIG. 3 shows an enlarged view of a section of a bearing surface of the axial bearing according to Fig. 2
  • Fig. 4 shows a perspective view of a section of the bearing surface of the axial bearing according to the invention according to a second embodiment
  • Fig. 5 shows a perspective view of a section of the bearing surface of the axial bearing according to the invention according to a third embodiment
  • Fig. 6 shows a perspective view of a section of the bearing surface of the axial bearing according to the invention according to a fourth embodiment
  • Fig. 7 shows a perspective view of a section of the bearing surface of the axial bearing according to the invention according to a fifth embodiment
  • Fig. 8 shows a basic representation of a lubricant channel of the axial bearing according to the invention in different shapes and sizes.
  • An exhaust gas turbocharger 1 according to the invention which has an axial bearing 2 according to the invention, essentially has a housing 3 with an exhaust gas guide section 4, a fresh air guide section 5 and a bearing section 6 and a rotor 7 with a turbine wheel 8, a compressor wheel 9 and a shaft 10 that connects the turbine wheel 8 to the compressor wheel 9 in a rotationally fixed manner.
  • the rotor 7 is rotatably accommodated in the housing 3 such that the turbine wheel 8 is arranged rotatably in the exhaust gas guide section 4, the compressor wheel 9 in the fresh air guide section 5 and the shaft 10 in the bearing section 6.
  • the shaft 10 is rotatably mounted in the bearing section 6 with the aid of at least one radial bearing 11 for absorbing radial forces and at least one axial bearing 2 for absorbing axial forces.
  • Fig. 1 illustrates the exhaust gas turbocharger 1 according to the invention according to a first exemplary embodiment, wherein the axial bearing 2 according to the invention is designed in the form of a sleeve.
  • the axial bearing 2, which is designed in the form of the sleeve, is formed integrally with the radial bearing 11.
  • the axial bearing 2 for supporting the rotatable shaft 10 comprises a first bearing body 12 which is firmly connected to the bearing section 6 and has a first sliding surface 13, and a second bearing body 14 which rotates with the shaft 10 and has a second sliding surface 15. Both the first bearing body 12 and the second bearing body 14 each have a central opening 16 within which the shaft 10 is received.
  • the first sliding surface 13 is positioned facing the second sliding surface 15, forming a lubricating gap.
  • the second sliding surface 15 is essentially designed as a flat sliding surface.
  • the first sliding surface 13 positioned facing the second sliding surface 15 is designed as a bearing surface in the form of a circular ring surface 17 with a surface profile 18, comprising an outer edge 19 and an inner edge 20.
  • first sliding surface 13 could also be designed as a substantially flat sliding surface, in which case the second sliding surface 15 would be designed as a bearing surface.
  • the first sliding surface 13 and the second sliding surface 15 could also be designed as a bearing surface, which would result in a significant improvement in the running properties of the axial bearing 2 and a significant reduction in the wear of the axial bearing 2.
  • a lubricant supply channel 21 is formed penetrating the axial bearing 2 in the radial direction, wherein the lubricant is supplied to the first sliding surface 13 via a lubricant channel 23.
  • the sliding surface 13 has four partial surfaces 22, which are formed in the shape of a circular segment, as illustrated by way of example in Fig. 2. Of course, more or fewer than four partial surfaces 22 could also be formed.
  • Each of the partial surfaces 22, which can also be referred to as wedge surfaces, has the lubricant channel 23, with a channel inlet 24 and a channel outlet 25 facing away from the channel inlet 24 for Lubricant supply to the first sliding surface 13.
  • Lubricant can enter the channel inlet 24 via the lubricant supply channel 21 and be guided to the first sliding surface 13 via the channel outlet 25.
  • the lubricant channel 23 is designed to extend in the longitudinal direction of the sleeve.
  • the first sliding surface 13 has a particle groove 26 with a first groove end 27 and a second groove end 28 facing away from the first groove end 27.
  • the channel outlet 25 and the first groove end 27, which in the present embodiment corresponds to a groove inlet 29 of the particle groove 26, are designed to overlap one another. In other words, this means that in the first embodiment shown, the channel outlet 25 corresponds to the groove inlet 29. Or, to put it in other words, the channel outlet 25 is designed to receive the first groove end 27 and vice versa.
  • the particle groove 26 is preferably designed to be inclined relative to the lubricant channel 23.
  • a groove axis 30 of the particle groove 26 is designed to be inclined relative to a channel axis 31 of the lubricant channel 23 by an angle a, as is illustrated by way of example in Fig. 4.
  • the second groove end 28 is formed in the radial direction on the outer edge 19, in the region of the partial surface 22, and is thus designed to be spaced apart from an extension of the lubricant channel 23 along its channel axis 31.
  • the angle a depends on an area of application of the exhaust gas turbocharger 1 and on particles present in the lubricant and varies in a range with a value of the angle a between 0° and 90°.
  • the particle groove 26 is preferably aligned such that the particles have a particle movement which corresponds to a “natural” flow direction which results from a radial movement of the axial bearing 2 and centrifugal forces of the particles.
  • the particle groove 26 is designed to extend straight in the radial direction.
  • Figures 2 and 3 illustrate the axial bearing 2 according to the invention in accordance with the first embodiment.
  • the first sliding surface 13 has the partial surface 22 having a wedge surface 32 and a locking surface 33.
  • the wedge surface 32 is inclined in the direction of rotation D, starting from the locking surface 33 towards the particle groove 26.
  • the first sliding surface 13 has four partial surfaces 22, each with a lubricant channel 23 and a particle groove 26.
  • the lubricant channel 23 has a triangular cross section.
  • the axial bearing 2 according to the invention has the lubricant channel 23 having the triangular cross section connected to the particle groove 26 which has a round cross section NQ, as shown in Fig. 47.
  • the particle groove 26 can be formed directly between the wedge surface 32 and the locking surface 33, as is illustrated by way of example in Fig. 4, wherein the axial bearing 2 according to the invention is shown in a second exemplary embodiment in Fig. 4. Likewise, the particle groove 26 could also be formed in the locking surface 33, spaced from the wedge surface 32, as is illustrated by way of example in Figs. 5 to 7, a third, a fourth and a fifth exemplary embodiment.
  • the axial bearing 2 has the particle groove 26 essentially in the form of a cylinder section through which flow can pass, wherein in an outlet region 34 of the particle groove 26, which includes the second groove end 28, a second groove cross section NQ2 of the particle groove 26 is larger than a first groove cross section NQ1 of the particle groove 26, for improved removal of the particles.
  • the groove inlet 29 is larger than the channel outlet 25, so that particles can be safely received.
  • the first groove end 27 and the second groove end 28 could be the same size. This is easy to produce, for example with the help of a bore.
  • the particle groove 26 has a groove cross-section NQ, whereby the first groove end 27 has a first groove cross-section NQ1 and the second groove end 28 has the second groove cross-section NQ2.
  • the first groove cross-section NQ1 and/or the second groove cross-section NQ2 can correspond to the groove cross-section NQ, or they can be designed differently.
  • a cross-section QK of the channel outlet 25 can correspond to the first groove cross-section NQ1 or the groove cross-section NQ, and vice versa.
  • the particle groove 26 is conical along its groove axis 30, with a round cross section NQ, wherein the first groove end 27 is larger than the second groove end 28.
  • the cross section NQ of the particle groove 26 could be elliptical, circular, oval or even asymmetrically round.
  • the particle groove 26 has the second groove cross section NQ2 with a value of zero at its second groove end 28.
  • the particle groove 26 has a conical shape of varying degrees so that individual requirements for particle removal can be taken into account. In other words, this means that the cross-sectional areas of the particle groove 26, both at the first groove end 27 and at the second groove end 28, are dimensioned in such a way that an individual type and size of particles can be discharged.
  • the axial bearing 2 has the lubricant channel 23 with a non-circular, asymmetrical and/or freely formed channel outlet 25, wherein a surface transition from the channel outlet 25 to the partial surface 22 is elastohydrodynamically improved for optimized lubricant supply.
  • the first sliding surface 13 is at least partially equipped with a microstructure, in particular in the area of at least one wedge surface 32 and/or locking surface 33.
  • the sliding surfaces 13, 15 also have at least partially a friction- and/or wear-reducing surface coating.
  • the axial bearing 2 can be manufactured in a short time. If the first sliding surface 13 has a larger number of lubricant channels 23 and a correspondingly larger number of wedge and locking surfaces 32, 33, then an increase in the number can be expected to result in a more even load on the locking surfaces 33 and thus a further reduction in wear. Overall, for example, with a number of twelve lubricant channels 23 and respectively twelve wedge and locking surfaces 32, 33, a hydrodynamic state in transient operation is reached more quickly than with a number of four lubricant channels 23, respectively four wedge and locking surfaces 32,
  • a shape and positioning of the particle groove 26 on the first sliding surface 13 are selected to bring about an optimal lubricant flow through the axial bearing 2 in such a way that a load-bearing capacity of the axial bearing 2, which should not be impaired, is taken into account.
  • the particle groove 26 is provided in the axial bearing 2, which is designed in the form of a sleeve, both on a first sleeve end face 35 designed towards the turbine wheel 8 and on a second sleeve end face 36 designed facing the compressor wheel 9.
  • the particle groove 26 can be produced, for example, by sintering or forging or by a machining process.
  • Fig. 8 shows a basic representation of the lubricant channel 23 in different sizes and shapes.
  • the lubricant channel 23 is shown in a triangular shape with a solid line, whereas it is shown in a dashed line in an elliptical shape, thus having an elliptical cross-section.
  • a smaller triangular lubricant channel 23 is shown than on the left side of the central opening 16.
  • a particle 37 is illustrated as an example.
  • an increase in the particle size capacity can be achieved in a simple manner by keeping the groove width NB constant and realizing the lubricant channel 23 in an elliptical shape, as shown in dashed lines.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Oil, Petroleum & Natural Gas (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Supercharger (AREA)
  • Sliding-Contact Bearings (AREA)

Abstract

L'invention concerne un palier axial (2) pour supporter un arbre rotatif (10), un premier corps de palier (12) étant relié de manière fixe à une partie de palier (6) d'un turbocompresseur à gaz d'échappement (1) et un second corps de palier (14) tournant avec l'arbre (10), au moins le premier corps de palier (12) possédant une première surface de coulissement (13) avec une surface annulaire circulaire (17) et avec un profil de surface (18), un espace de lubrification avec du lubrifiant étant formé entre la première surface de coulissement (13) et une surface de coulissement (15) du deuxième corps de palier (14), et un canal de lubrifiant (23) étant formé dans le premier corps de palier (12), possédant une entrée de canal (24) et une sortie de canal (25) pour fournir du lubrifiant à la surface annulaire circulaire (17), la première surface de coulissement (13) étant formée sur une face d'extrémité d'un manchon, et la première surface de coulissement (13) étant conçue avec au moins une surface de coin (32) et une surface de détente (33), la surface de coin (32) étant inclinée à partir de la surface de détente (33). La première surface de coulissement (13) présente une rainure de particule (26) qui est formée entre la surface de coin (32) et la surface de détente (33) et présente une première extrémité de rainure (27) et une seconde extrémité de rainure (28) opposée à la première extrémité de rainure (27), la sortie de canal (25) étant formée pour recevoir la première extrémité de rainure (27), et la seconde extrémité de rainure (28) étant formée dans la direction radiale au moins au niveau d'un premier bord externe (19) de la surface annulaire circulaire (17) ou au-delà de celle-ci, et une première section transversale de rainure (NQ1) de la première extrémité de rainure (27) étant plus grande ou plus petite qu'une seconde section transversale de rainure (NQ2) de la seconde extrémité de rainure (28), et/ou la rainure de particule (26) possédant une section transversale ronde (NQ), et le canal de lubrifiant (23) possédant une section transversale triangulaire ou elliptique.
PCT/DE2023/100830 2022-11-15 2023-11-07 Palier axial pour supporter un arbre rotatif et turbocompresseur à gaz d'échappement possédant un palier axial WO2024104529A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102022130239 2022-11-15
DE102022130239.3 2022-11-15

Publications (1)

Publication Number Publication Date
WO2024104529A1 true WO2024104529A1 (fr) 2024-05-23

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PCT/DE2023/100829 WO2024104528A1 (fr) 2022-11-15 2023-11-07 Palier axial pour supporter un arbre rotatif et turbocompresseur à gaz d'échappement ayant un palier axial
PCT/DE2023/100830 WO2024104529A1 (fr) 2022-11-15 2023-11-07 Palier axial pour supporter un arbre rotatif et turbocompresseur à gaz d'échappement possédant un palier axial

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PCT/DE2023/100829 WO2024104528A1 (fr) 2022-11-15 2023-11-07 Palier axial pour supporter un arbre rotatif et turbocompresseur à gaz d'échappement ayant un palier axial

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Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1400440A1 (de) 1961-09-28 1969-04-03 Thompson Ramo Wooldridge Inc Lager fuer schnellaufende Wellen
EP0329193A1 (fr) * 1985-10-22 1989-08-23 Reliance Electric Industrial Company Construction de palier notamment palier axial
EP0887516A2 (fr) * 1997-06-26 1998-12-30 Ishikawajima-Harima Heavy Industries Co., Ltd. Palier de poussée pour une turbosoufflante
WO1999007982A1 (fr) 1997-08-06 1999-02-18 Alliedsignal Inc. Systeme de palier integre pour turbocompresseur
DE102011085681A1 (de) * 2011-11-03 2013-05-08 Abb Turbo Systems Ag Hydrodynamisches Axiallager
DE202013105567U1 (de) * 2013-04-24 2014-01-28 E. Winkemann Gmbh Anlaufscheibe mit Schmiermitteltaschen
US20180087518A1 (en) * 2016-09-24 2018-03-29 Borgwarner Inc. Turbocharger thrust bearing and manufacturing method
DE112017004889T5 (de) 2016-09-29 2019-06-13 Ihi Corporation Lagerstruktur und Turbolader

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110454430B (zh) 2018-05-07 2023-03-28 博格华纳公司 内燃机涡轮增压器

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1400440A1 (de) 1961-09-28 1969-04-03 Thompson Ramo Wooldridge Inc Lager fuer schnellaufende Wellen
EP0329193A1 (fr) * 1985-10-22 1989-08-23 Reliance Electric Industrial Company Construction de palier notamment palier axial
EP0887516A2 (fr) * 1997-06-26 1998-12-30 Ishikawajima-Harima Heavy Industries Co., Ltd. Palier de poussée pour une turbosoufflante
WO1999007982A1 (fr) 1997-08-06 1999-02-18 Alliedsignal Inc. Systeme de palier integre pour turbocompresseur
DE102011085681A1 (de) * 2011-11-03 2013-05-08 Abb Turbo Systems Ag Hydrodynamisches Axiallager
DE202013105567U1 (de) * 2013-04-24 2014-01-28 E. Winkemann Gmbh Anlaufscheibe mit Schmiermitteltaschen
US20180087518A1 (en) * 2016-09-24 2018-03-29 Borgwarner Inc. Turbocharger thrust bearing and manufacturing method
DE112017004889T5 (de) 2016-09-29 2019-06-13 Ihi Corporation Lagerstruktur und Turbolader

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