WO2020108951A1 - Palier à patins oscillants - Google Patents

Palier à patins oscillants Download PDF

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Publication number
WO2020108951A1
WO2020108951A1 PCT/EP2019/080649 EP2019080649W WO2020108951A1 WO 2020108951 A1 WO2020108951 A1 WO 2020108951A1 EP 2019080649 W EP2019080649 W EP 2019080649W WO 2020108951 A1 WO2020108951 A1 WO 2020108951A1
Authority
WO
WIPO (PCT)
Prior art keywords
bearing
tilting
bearing sleeve
webs
segment
Prior art date
Application number
PCT/EP2019/080649
Other languages
German (de)
English (en)
Inventor
Kai-Henning Brune
Dietrich Klauk
Tim Maier
Original Assignee
Robert Bosch 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 Robert Bosch Gmbh filed Critical Robert Bosch Gmbh
Publication of WO2020108951A1 publication Critical patent/WO2020108951A1/fr

Links

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
    • F16C17/02—Sliding-contact bearings for exclusively rotary movement for radial load only
    • F16C17/03—Sliding-contact bearings for exclusively rotary movement for radial load only with tiltably-supported segments, e.g. Michell bearings
    • F16C17/035—Sliding-contact bearings for exclusively rotary movement for radial load only with tiltably-supported segments, e.g. Michell bearings the segments being integrally formed with, or rigidly fixed to, a support-element
    • 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
    • F16C32/00—Bearings not otherwise provided for
    • F16C32/06—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings
    • F16C32/0603—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings supported by a gas cushion, e.g. an air cushion
    • 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
    • F16C33/1005—Construction relative to lubrication with gas, e.g. air, as lubricant
    • 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
    • F16C2240/00—Specified values or numerical ranges of parameters; Relations between them
    • F16C2240/30—Angles, e.g. inclinations

Definitions

  • the invention relates to a tilting segment bearing for supporting a shaft.
  • Tilt segment bearings are mainly used oil-lubricated at low and medium speeds or circumferential speeds up to approx. 100 m / s.
  • Air-lubricated tilting segment bearings can be used for higher peripheral speeds if the bearing load requirements are not too high. Due to the lower viscosity of the air compared to oil, the lubrication gap heights in the air-lubricated tilting segment bearings are significantly smaller than in the oil-lubricated bearings. In some cases, the lubrication gap heights are in the order of 10pm and are therefore 5 times smaller than with oil-lubricated bearings.
  • the narrower bearing gaps place high demands on the dimensional accuracy of the bearing surface for the shaft to be supported.
  • DE 32 25 423 C2 discloses a tilting segment bearing with a bearing sleeve and a plurality of tilting segments arranged within the bearing sleeve.
  • the tilting segments are each mounted in the bearing sleeve by means of a pin.
  • the tilting segment bearing according to the invention supports a shaft more robustly and thermally and dynamically more stable.
  • the tilting segment bearing has a bearing sleeve and a plurality of tilting segments arranged within the bearing sleeve.
  • the tilting segments are each connected to the bearing sleeve by means of a web, preferably monolithically.
  • each tilting segment is preferably connected monolithically to the bearing sleeve by means of exactly one web.
  • the web is very thin compared to the tilting segment, for example 20 times thinner when viewed in the circumferential direction, so that the tilting segment is connected to the bearing sleeve almost at certain points.
  • connection of the tilting segment to the bearing sleeve is made very elastic, the tilting segment can tilt around the web, whereby rotor dynamic accelerations can be compensated for, in particular in combination with a bearing sleeve that is not pressed in over the entire circumference.
  • notches are formed on an outer circumference of the bearing sleeve opposite the webs. There is preferably one notch per web. The notches reduce the rigidity of the bearing sleeve in the area of the webs. As a result, thermal expansions and displacements due to a press-in process of the tilting segment bearing can be specifically designed so that a bearing gap between the tilting segments and the shaft remains comparatively constant even over the assembly and operating states.
  • a plurality, preferably three, fastening surfaces are preferably formed on an outer circumference of the bearing sleeve.
  • the tilting segment bearing or the bearing sleeve is thus only pressed into the housing on the fastening surfaces, screwed axially or firmly connected to the housing in another way.
  • the press fit or the fastening is therefore not carried out over the entire outer circumference of the bearing sleeve, but only on the fastening surfaces. In the case of press-in, it is not the entire outer circumference that experiences the maximum radial displacement inwards, but only the fastening surfaces.
  • the areas of the bearing ring that are exposed to the outside are bent outwards due to the pressing forces, as a result of which the webs and thus also the tilting segments are displaced radially outward, which in turn can compensate for the effect of the pressing forces on the radial displacement of the tilting segments.
  • the number of fastening surfaces thus preferably corresponds to the number of tilting segments or the number of corresponding webs.
  • bearing sleeve In an alternative advantageous embodiment, several, preferably three, bores for receiving screws are formed in the bearing sleeve.
  • the bearing sleeve is thus fixed in the housing in the area of the bores.
  • the attachment is not executed over the entire circumference of the bearing sleeve, but only in the area of the bores.
  • the number of bores preferably corresponds to the number of tilting segments or the number of corresponding webs. In this version, no press-in forces have to be compensated; compensation focuses on thermal expansion.
  • recesses are formed on an inner circumference of the bearing sleeve opposite the fastening surfaces or the bores.
  • a recess is preferably provided for each fastening surface or for each bore.
  • the recesses reduce the rigidity of the bearing sleeve in the area of the fastening surfaces or in the area of the bores.
  • the stiffness of the facial expressions can be specifically adjusted with the recesses in order to compensate for thermal expansion and displacements due to a pressing-in process of the tilting segment bearing, so that a bearing gap between the tilting segments and the shaft remains comparatively constant even over the assembly and operating states.
  • the recesses and notches can of course also be combined if necessary.
  • transition webs are formed on an outer circumference of the bearing sleeve, on which the bearing sleeve is connected to a bearing ring surrounding it.
  • the bearing ring, the transition webs, the bearing sleeve, the tilting segments and the webs are preferably monolithic. The tilting segment bearing can therefore be pressed or screwed into the housing on the bearing ring.
  • transition webs which in the previous versions were the fastening surfaces
  • the inward-facing areas of the tilting segment bearing such as webs and tilting segments
  • the number of transition webs preferably corresponds to the number of tilting segments or the number of corresponding webs, so that the individual tilting segments behave homogeneously.
  • recesses are formed on an inner circumference of the bearing sleeve opposite the transition webs. There is preferably a recess per transition web.
  • the recesses reduce the stiffness of the bearing sleeve in the area of the transition webs, thereby specifically reducing the stiffness the facial expressions can be constructed. As a result, thermal expansion of the tilting segment bearing can be better compensated to the extent that a bearing gap between the tilting segments and the shaft remains comparatively constant even over the assembly and operating states.
  • a web is arranged between two fastening surfaces or between two transition webs or between two bores in an angular direction of the tilting segment bearing, depending on the version with or without a bearing ring.
  • a web is not followed by any material (fastening surface or transition web), but rather an exemption surface arranged between them, so that the outer circumference of the bearing sleeve in the region of the web shrinks less than on the fastening surfaces or on the transition webs.
  • the web is arranged in the middle between two fastening surfaces or two bores.
  • the web is accordingly arranged centrally between two transition webs.
  • the webs have an off-center angular offset to the fastening surfaces or to the bores or to the transition webs. This means that a web has different distances clockwise and counterclockwise to the next two fastening surfaces or to the next two transition webs or to the next two bores.
  • the web due to the rigidity of the bearing sleeve and the contact forces of the press fit acting on the fastening surfaces - or the cutting forces acting on the transition webs - the web is not only displaced radially inward, but also slightly tilted tangentially. This creates a tilt pretension of the tilt segment. This is particularly advantageous if the formation of a wedge-shaped bearing gap is to be additionally supported.
  • the tilting segments are arranged off-center on the associated web. This means that the two ends of a tilting segment are at a different distance from the corresponding web. This supports the formation of the lubricating wedge in the bearing gap during operation of the tilting segment bearing.
  • the tilting segment bearing is preferably an air-lubricated tilting segment bearing according to an embodiment of the invention.
  • FIG. 1 shows a schematic cross-sectional view of a tilting segment bearing, only the essential areas being shown;
  • FIG. 2 shows a schematic cross-sectional view of a further tilting segment bearing, only the essential areas being shown;
  • FIG. 3 shows a schematic cross-sectional view of a tilting segment bearing in a further embodiment, only the essential areas being shown;
  • FIG. 4 shows a schematic cross-sectional view of a tilting segment bearing in yet another embodiment, only the essential areas being shown;
  • FIG. 5 shows a schematic cross-sectional view of a tilting segment bearing in yet another embodiment, only the essential areas being shown.
  • FIG. 6 shows a schematic cross-sectional view of a tilting segment bearing in yet another embodiment, only the essential areas being shown.
  • FIG. 1 shows a schematic cross-sectional view of an exemplary embodiment of a tilting segment bearing 1, which supports a shaft 20 radially, only the essential areas being shown.
  • the tilting segment bearing 1 has a bearing sleeve 2 and preferably three tilting segments 3 at a certain distance from an inner circumference 2b of the bearing sleeve 2.
  • the individual tilting segments 3 are each connected to the bearing sleeve 2 by means of exactly one web 4; the bearing sleeve 2, the tilting segments 3 and the webs 4 are preferably formed in one piece, that is to say monolithically.
  • Fastening surfaces 5 for arranging the tilting segment bearing 1 in a housing are formed on an outer circumference 2a of the bearing sleeve 2.
  • the fastening surfaces 5 therefore alternate over the circumference with release surfaces 5a, which have a smaller diameter.
  • the tilting segment bearing 1 is pressed into the housing on the fastening surfaces 5.
  • the webs 4, viewed in an angular direction f of the tilting segment bearing 1 are positioned between the fastening surfaces 5. This means that the bearing sleeve 2 and an exemption surface 5a follow a web 4 in the radial direction outwards, so that the pressing in on the fastening surfaces 5 only results in a comparatively small radial displacement of the webs 4.
  • the press fit between the housing and the bearing sleeve 2 acts only on the mounting surfaces 5, but not on the release surfaces 5a.
  • the outer circumference 2a of the bearing sleeve 2 is thus reduced in diameter, particularly in the area of the fastening surfaces 5.
  • the diameter of the outer circumference 2a bends outward in the region of the relief surfaces 5a.
  • the deformation of the bearing sleeve 2 in the area of the webs 4 is thus reduced, and thus also the radial displacement of the tilting segments 3.
  • the positioning of the tilting segments 3 with respect to the shaft 20 is thus less changed by the pressing of the tilting segment bearing 1 into the housing. Ideally, the position of the tilting segments 3 remains almost the same regardless of the thickness of the press fit.
  • the webs 4 - viewed in the angular direction f - are arranged centrally between two fastening surfaces 5, so that a first angle a of the web 4 to the next fastening surface 5 in the clockwise direction is as large as a second angle ⁇ of the web 4 to the next Mounting surface 5 counterclockwise; the webs 4 are thus arranged in the middle of an exemption area 5a.
  • the tilting segments 3 are arranged off-center on the associated web 4. This means that a first arc length 3_1 of the tilting segment 3 from one end 3a to the respective web 4 is smaller than a second arc length 3_2 from the same web 4 to the other end 3b of the same tilting segment 3.
  • the third angle g from one end 3a of the tilting segment 3 to its web 4 is smaller than the fourth angle d from the web 4 to the other end 3b of the tilting segment 3;
  • FIG. 2 shows a schematic cross-sectional view of a further exemplary embodiment for a tilting segment bearing 1, only the essential areas being shown.
  • the webs 4 have an eccentric angular offset to the fastening surfaces 5. That is, viewed in the angular direction f, the first angle a of the web 4 to the next fastening surface 5 in the clockwise direction is greater or smaller than the second angle ⁇ of the web 4 to the next fastening surface 5 in the counterclockwise direction, preferably several times larger or smaller .
  • the tilting segment 3 can be tilted or offset tangentially, specifically by pressing in or thermal expansion.
  • the tilting segment bearing 1 is preferably monolithic.
  • the bearing gap 7 narrowing in the direction of rotation between the tilting segment 3 and the shaft 20 due to the inclination or tangential displacement leads to a better formation of the lubricating film in the operating state; for example, a kind of lubrication pad or lubrication wedge is formed in the bearing gap 7 by the gas or the ambient air.
  • the tilting segment 3 By connecting the tilting segments 3 in the center of the clearance area 5a, depending on the temperature in the bearing sleeve 2, the tilting segment 3 is pulled radially outward (in the case of one-piece tilting segment bearings 1) or the support point or the web 4 moves outward (in the case of multi-parting tilting segment bearings 1) .
  • a larger bearing gap 7 is created between the tilting segment 3 and the shaft 20 than without this measure.
  • the thermal expansions of the shaft 20 and the tilting segments can be done in this way 3 are compensated so that a largely uniform bearing gap 7 is established over all operating points.
  • the tilting segment 3 can additionally be tilted, which leads to a specific prestressing of the tilting segment 3 to the shaft 20. This helps in the formation of the lubricating film and thus to make the tilting segment bearing 1 dynamically more stable.
  • the tilting segment bearing 1 is particularly preferably monolithic.
  • the tilting segment 3 is pulled outwards when the tilting segment bearing 1 is pressed in and tilts clockwise, that is to say in the angular direction f.
  • the shaft 20 then preferably also rotates in the angular direction f, so that the bearing gap 7 is reduced in the running direction via the tilting segment 3.
  • FIG. 3 shows a schematic cross-sectional view of a still further exemplary embodiment of a tilting segment bearing 1, only the essential areas being shown. In the following, only the differences from the explanations according to Fiq.1 or Fiq.2 are discussed.
  • the heating of the tilting segment bearing 1 essentially results from the bearing gap 7 between the tilting segments 3 and the shaft 20, and therefore the shaft 20 and the tilting segments 3 usually have the highest temperatures, it is advantageous to have the best possible thermal connection of the bearing sleeve 2 to the Ensure tilting segments 3 in order to optimize the heat dissipation to the outside, as is shown in the embodiment of FIG. 3;
  • the bearing sleeve 2 is separated from the tilting segments 3 on its inner circumference 2b outside the webs 4 only by a kind of thin cut 8.
  • the thin cut 8 preferably has a width of at most 0.1 mm, preferably even only at most 0.05 mm. This thin cut 8 is preferably produced by eroding.
  • Fig. 4 shows a schematic cross-sectional view of yet another exemplary embodiment of a tilting segment bearing 1, only the essential areas being shown.
  • the tilting segment bearing 1 has recesses 51 formed on the inner circumference 2b of the bearing sleeve 2, which are arranged opposite the fastening surfaces 5.
  • a recess 51 is preferably also formed on the inner circumference 2b opposite each fastening surface 5.
  • notches 41 are formed on the outer circumference 2a of the bearing sleeve 2, preferably exactly opposite to the webs 4.
  • the connection of the webs 4 to the bearing sleeve 2 is made very soft.
  • the areas of the bearing sleeve 2 between the webs 4 or between the notches 41 thus bend comparatively less strongly and the corresponding thermal expansion is largely implemented by evading the connection of the webs 4 - and thus also the tilting segments 3.
  • a notch 41 is thus preferably also formed on the outer circumference 2a opposite each web 4.
  • the recesses 51 and notches 41 can be used separately or together in the previous exemplary embodiments in order to intensify the effect of compensating for expansions by heat or pressing.
  • the effect of the recesses 51 and notches 41 is as follows: In order to improve the bending line, the points that are supposed to be particularly soft are deliberately weakened by removing material - that is to say through the recesses 51 or notches 41, and thereby form solid-state joints in the Bearing sleeve 2 out.
  • the bearing sleeve 2 thus has a significantly lower rigidity in the areas of these solid joints than in the areas between two solid joints.
  • the heat or press-in compensation according to the invention can thereby be increased significantly again and set in a targeted manner.
  • the tilting segment bearing 1 has a bearing ring 9 which surrounds the bearing sleeve 2 and is preferably made monolithically with it.
  • the bearing ring 9 is connected to the bearing sleeve 2 on the former fastening surfaces 5 (from the embodiments in FIGS. 1 to 4) and virtually replaces part of the housing.
  • the bearing sleeve 2 is thus also connected to the bearing ring 9 comparatively softly, so that displacements from thermal expansion and press-in processes can be compensated very well.
  • the pressing forces can be absorbed by the bearing ring 9, which is preferably very stiff, and thus have no influence on the bearing gap 7. That is, the influence of the pressing forces on the other components of the tilting segment bearing 1 can be minimized or eliminated by the bearing ring 9.
  • the fastening surfaces 5 of the previous exemplary embodiments are referred to as transition webs 52, on which the bearing sleeve 2 is preferably connected monolithically to the bearing ring 9.
  • the outer circumference 2a of the bearing sleeve can also be made non-cylindrical, for example polygonal as shown in FIG. 5; this can have a further positive effect on heat compensation.
  • the recesses 51 and notches 41 can optionally be used in order to specifically reduce the rigidity at the transitions from the bearing ring 9 to the bearing sleeve 2 or the bearing sleeve 2 to the tilting segments 3.
  • FIG. 6 shows a schematic cross-sectional view of yet another exemplary embodiment of a tilting segment bearing 1, only the essential areas being shown.
  • the execution according to Fiq.6 is similar to the execution according to Fiq.2, however the bearing sleeve 2 is now attached to the housing (not shown) by means of screw connections.
  • three bores 25 are formed in the bearing sleeve 2, which run in the axial direction of the shaft 20.
  • Corresponding screws can be inserted into the bores 25, so that the bearing sleeve 2 with the housing can be clamped axially. This means that no radial forces act on the bearing due to this attachment.
  • the formation of the fastening surfaces 5 on the outer circumference 2a is no longer necessary in this embodiment.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mounting Of Bearings Or Others (AREA)

Abstract

L'invention concerne un palier à patins oscillants (1) comprenant une douille-palier (2) et plusieurs patins oscillants (3) disposés dans la douille-palier (2). Les patins oscillants (3) sont raccordés respectivement au moyen d'un élément de liaison (4), de préférence de manière monolithique, à la douille-palier (2).
PCT/EP2019/080649 2018-11-28 2019-11-08 Palier à patins oscillants WO2020108951A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102018220452.7A DE102018220452A1 (de) 2018-11-28 2018-11-28 Kippsegmentlager
DE102018220452.7 2018-11-28

Publications (1)

Publication Number Publication Date
WO2020108951A1 true WO2020108951A1 (fr) 2020-06-04

Family

ID=68531546

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2019/080649 WO2020108951A1 (fr) 2018-11-28 2019-11-08 Palier à patins oscillants

Country Status (2)

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DE (1) DE102018220452A1 (fr)
WO (1) WO2020108951A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102020213827A1 (de) 2020-11-03 2022-05-05 Mtu Friedrichshafen Gmbh Gleitlagervorrichtung und Maschinenanordnung mit einer solchen Gleitlagervorrichtung

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2250546A (en) * 1936-09-10 1941-07-29 Michell Anthony George Maldon Bearing
DE3225423C2 (de) 1981-07-07 1986-11-27 Nuovo Pignone S.P.A., Florenz/Firenze Radial-Kippsegmentlager
WO1992003667A1 (fr) * 1990-08-24 1992-03-05 Ide Russell D Palier monte sur support autopositionneur, et ensemble palier/arbre comprenant un tel palier
WO2015046887A1 (fr) * 2013-09-24 2015-04-02 (주)삼본정공 Palier en matière plastique fonctionnel
DE102017202740A1 (de) * 2017-02-21 2018-08-23 Robert Bosch Gmbh Kippsegmentlager und Verfahren zur Herstellung eines Kippsegmentlagers

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3544392A1 (de) * 1985-12-14 1987-06-19 Kloeckner Humboldt Deutz Ag Aerodynamisches gleitlager
US5743654A (en) * 1987-05-29 1998-04-28 Kmc, Inc. Hydrostatic and active control movable pad bearing
US7497627B2 (en) * 2004-06-07 2009-03-03 Honeywell International Inc. Thrust bearing
EP2187072B1 (fr) * 2008-11-07 2012-09-12 General Electric Company Palier souple à gaz hybride utilisant des amortisseurs de treillis métallique
WO2013042489A1 (fr) * 2011-09-22 2013-03-28 プラス精機株式会社 Dispositif de changement de pas d'objets empilés

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2250546A (en) * 1936-09-10 1941-07-29 Michell Anthony George Maldon Bearing
DE3225423C2 (de) 1981-07-07 1986-11-27 Nuovo Pignone S.P.A., Florenz/Firenze Radial-Kippsegmentlager
WO1992003667A1 (fr) * 1990-08-24 1992-03-05 Ide Russell D Palier monte sur support autopositionneur, et ensemble palier/arbre comprenant un tel palier
WO2015046887A1 (fr) * 2013-09-24 2015-04-02 (주)삼본정공 Palier en matière plastique fonctionnel
DE102017202740A1 (de) * 2017-02-21 2018-08-23 Robert Bosch Gmbh Kippsegmentlager und Verfahren zur Herstellung eines Kippsegmentlagers

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