WO2020108952A1 - Palier à patins oscillants - Google Patents

Palier à patins oscillants Download PDF

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Publication number
WO2020108952A1
WO2020108952A1 PCT/EP2019/080652 EP2019080652W WO2020108952A1 WO 2020108952 A1 WO2020108952 A1 WO 2020108952A1 EP 2019080652 W EP2019080652 W EP 2019080652W WO 2020108952 A1 WO2020108952 A1 WO 2020108952A1
Authority
WO
WIPO (PCT)
Prior art keywords
tilting
bearing
press
fit
web
Prior art date
Application number
PCT/EP2019/080652
Other languages
German (de)
English (en)
Inventor
Guido Daimer
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 WO2020108952A1 publication Critical patent/WO2020108952A1/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
    • 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

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.
  • the web is very narrow compared to the tilting segment, for example 20 times narrower 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 tip over the web; however, thermal expansions and relative displacements can also be better compensated for, in particular in combination with a bearing sleeve that is not pressed in over the entire circumference.
  • a plurality, preferably three, press-fit surfaces are preferably formed on an outer circumference of the bearing sleeve.
  • the tilting segment bearing or the bearing sleeve is pressed into a housing on the press-fit surfaces.
  • the press fit is therefore not carried out over the entire outer circumference of the bearing sleeve, but only on the press fit surfaces.
  • it is not the entire outer circumference that experiences the maximum radial displacement inwards during the pressing in, but only the press-fit surfaces; the radial displacement of the webs and thus also the tilting segments due to the pressing in can thus be reduced, in particular with increasing distance from the press-fitting surfaces in the circumferential direction or angular direction.
  • the number of press-fit areas thus preferably corresponds to the number of tilting segments or the number of corresponding webs.
  • a web is arranged between two press-fit surfaces in an advantageous embodiment in an angular direction of the tilting segment bearing. This means that radially outwards, a web is not followed by a press-fit area, but rather by a clearance area arranged between them, so that the outer circumference in the area of the web shrinks less than at the press-fit areas.
  • the web is arranged in the middle between two press-fit surfaces. This maximizes the effect described above and consequently minimizes the radial displacement of the web due to the pressing. Corresponding thermal relative displacements are also minimized as a result.
  • the tilting segment bearing is thus designed to be functionally more stable and robust.
  • the webs have an eccentric angular offset to the press-fit surfaces. That means a footbridge has different distances clockwise and counterclockwise to the next two press fit surfaces.
  • 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 there is to be a non-homogeneous lubrication gap between the shaft and the tilting segment; the lubricating gap should preferably decrease in the direction of rotation of the shaft, so that a type of lubricating wedge is formed.
  • the ends of the tilting segments interact radially outward with stop surfaces formed on the bearing sleeve.
  • the stop surfaces thus form a type of radial bearing, in particular during assembly, for the tilting segments in the outward direction. This prevents excessive deformation of the web.
  • the stop surfaces should preferably prevent the tilting segments from deflecting too strongly only when the shaft is being assembled. In operation, no contact should preferably be made here.
  • 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 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; 3 shows a schematic cross-sectional view of a tilting segment bearing in a further 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.
  • the individual tilting segments 3 are each connected to the bearing sleeve 2 by means of a web 4, preferably the bearing sleeve 2, the tilting segments 3 and the webs 4 are formed in one piece, that is to say monolithically.
  • press-fit surfaces 5 for the arrangement of the tilting segment bearing 1 are formed in a housing (not shown). Accordingly, the press-fit areas 5 alternate over the circumference with release areas 5a, which have a smaller diameter. Ideally, the tilting segment bearing 1 is pressed into the housing at the press-fit surfaces 5.
  • the webs 4, viewed in an angular direction f of the tilting segment bearing 1 are positioned between the press-fit surfaces 5. This means that the bearing sleeve 2 and a clearance surface 5a follow a web 4 in the radial direction outwards, so that the pressing in on the press-fit surfaces 5 results in only a comparatively small radial displacement of the webs 4.
  • the press fit between the housing and the bearing sleeve 2 acts only on the press-fit 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 press-fit surfaces 5; the diameter of the outer circumference 2a in the area of the clearance areas 5a is reduced less.
  • 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.
  • the position of the tilting segments 3 remains almost the same regardless of the thickness of the press fit. With temperature changes find linear Expansions instead, so that the influence on the change in gap between the tilting segments 3 and the shaft 20 still largely depends on the respective temperature expansion coefficients of the material pairing of the shaft and tilting segment bearing.
  • the webs 4 - viewed in the angular direction f - are preferably arranged centrally between two press-fit surfaces 5, so that a first angle a of the web 4 to the next press-fit surface 5 in the clockwise direction is as large as a second angle ⁇ of the web 4 to the next Press fit surface 5 counterclockwise.
  • stop surfaces 6 are formed on an inner circumference 2b of the bearing sleeve 2, which limit a radial displacement of the ends 3a, 3b of the tilting segments 3 to the outside.
  • a stop surface 6 with two ends 3a, 3b of two adjacent tilting segments 3 can cooperate.
  • the number of stop surfaces 6 is preferably the same as the number of tilting segments 3, particularly preferably three stop surfaces 6.
  • 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. in the In the following, however, only the differences to the execution according to Fiq.1 will be discussed.
  • the press-fit surfaces 5 are designed over a further circumference of the outer circumference 2a, the circumference of the relief surfaces 5a is consequently reduced. Viewed in the radial direction, the bearing sleeve 2 and a press-fit surface 5 thus follow a stop surface 6.
  • the stop surfaces 6 are designed to be very stiff and positioned robustly with small tolerances; when pressed in, this preferably results in a purely radial displacement of the stop surfaces 6.
  • 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, however, only the differences from the embodiments according to FIGS. 1 and 2 will be discussed.
  • the webs 4 have an off-center angular offset to the press-fit surfaces 5. That is, viewed in the angular direction f, the first angle a of the web 4 to the next press-fit surface 5 in the clockwise direction is greater or smaller than the second angle ⁇ of the web 4 to the next press-fit surface 5 in the counterclockwise direction, preferably several times larger or smaller .
  • the tilting segment 3 can be set obliquely or displaced tangentially in its pressed-in state. This helps to make the tilting segment bearing 1 dynamically stable during operation; to this end, the tilting segment bearing 1 is preferably monolithic.
  • the gap between tilting segment 3 and shaft 20 which narrows in the direction of rotation due to the inclination or tangential displacement leads to particularly favorable tribological conditions in the operating state; for example, a kind of lubrication pad or lubrication wedge is formed in the gap by the gas or the ambient air.
  • the abutment surfaces 6 avoid excessive deformation or displacement of the webs 4, since they limit their freedom of tilt movement. This is also advantageous as protection during the assembly of the shaft 20 in the tilting segment bearing 1. When installed, the tilting segments 3 preferably cause self-locking.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mounting Of Bearings Or Others (AREA)
  • Sliding-Contact Bearings (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/EP2019/080652 2018-11-28 2019-11-08 Palier à patins oscillants WO2020108952A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102018220449.7A DE102018220449A1 (de) 2018-11-28 2018-11-28 Kippsegmentlager
DE102018220449.7 2018-11-28

Publications (1)

Publication Number Publication Date
WO2020108952A1 true WO2020108952A1 (fr) 2020-06-04

Family

ID=68581765

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2019/080652 WO2020108952A1 (fr) 2018-11-28 2019-11-08 Palier à patins oscillants

Country Status (2)

Country Link
DE (1) DE102018220449A1 (fr)
WO (1) WO2020108952A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
NL2027506B1 (en) * 2021-02-05 2022-09-06 Johannes Hendricus Wilhelmus Nabuurs Martinus Tilting pad bearing, assembly of a construction element and such a bearing, and a method for providing a journal opening having a desired cross-section

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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
US5911511A (en) * 1997-09-26 1999-06-15 Alliedsignal Inc. Tilting pad foil thrust and journal bearings
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

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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
US5911511A (en) * 1997-09-26 1999-06-15 Alliedsignal Inc. Tilting pad foil thrust and journal bearings
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

Also Published As

Publication number Publication date
DE102018220449A1 (de) 2020-05-28

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