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WO2017100555A1 - Enveloppe de palier lisse dotée d'éléments anti-rotation - Google Patents

Enveloppe de palier lisse dotée d'éléments anti-rotation Download PDF

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Publication number
WO2017100555A1
WO2017100555A1 PCT/US2016/065803 US2016065803W WO2017100555A1 WO 2017100555 A1 WO2017100555 A1 WO 2017100555A1 US 2016065803 W US2016065803 W US 2016065803W WO 2017100555 A1 WO2017100555 A1 WO 2017100555A1
Authority
WO
WIPO (PCT)
Prior art keywords
semi
cylindrical
recess
shell
axial end
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/US2016/065803
Other languages
English (en)
Inventor
Bertrand DEPRES
Imad ISSAAD
Baptiste LEFEBVRE
Marc Provence
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
GGB Inc
Original Assignee
GGB Inc
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 GGB Inc filed Critical GGB Inc
Publication of WO2017100555A1 publication Critical patent/WO2017100555A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/0404—Details or component parts
    • F04B1/0408—Pistons
    • 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
    • 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
    • F16C33/08—Attachment of brasses, bushes or linings to the bearing housing

Definitions

  • Plain bearing shells have previously been used as an interface layer between, for example, a piston and a roller or shaft disposed in the recess of a piston. Plain bearing shells can help to reduce friction between a rotating roller or shaft and the walls of the recess in the piston, as well as improve alignment of the roller or shaft within the recess. However, in some instances, the plain bearing shell begins to rotate as the roller or shaft rotates, thereby potentially causing friction and or alignment issues. Accordingly, a need exists for plain bearing shells that do not rotate when serving as an interface layer between pistons and rollers or shafts.
  • a plain bearing shell with anti-rotation features is described.
  • the plain bearing shell can have a generally semi-cylindrical geometry.
  • a recess is formed at each axial end of the plain bearing shell.
  • the piston recess in which the plain bearing shell is disposed may include protrusions sized and shaped to mate with the recess at the axial ends of the plain bearing shell to thereby prevent rotation of the plain bearing shell when the plain bearing shell is disposed in the piston recess.
  • the plain bearing shell further includes thrust bearings at the axial ends of the plain bearing shell.
  • a plain bearing shell has a generally semi- cylindrical geometry and further includes radially outwardly angled tabs formed in a portion of the circumferential ends of the plain bearing shell. The tabs provide an edge that is perpendicular to the axis of the plain bearing shell.
  • the piston recess includes female imprints shaped and sized to receive the tabs and thereby prevent rotation of the plain bearing shell and assist with axial alignment of the plain bearing shell in the piston recess.
  • the plain bearing shell can also include thrust bearing extending from the axial ends of the plain bearing shell to provide an interface between axial ends of the roller or shaft and the axial ends of the piston recess
  • Figures 1 a-1 e illustrate plain bearing shells with anti-rotation features according to various embodiments described herein;
  • Figures 2a-2e illustrate plain bearing shells with anti-rotation features according to various embodiments described herein;
  • Figures 3a and 3b illustrate plain bearing shells with anti-rotation features according to various embodiments described herein;
  • Figure 4 illustrates plain bearing shells with anti-rotation features according to various embodiments described herein.
  • a plain bearing shell 100 is generally adapted to reside within a recess of a piston 2.
  • the piston 2 may be, for example, for use with a radial piston engine.
  • a roller or a shaft 3 (shown in phantom) may then be housed within plain bearing shell 100.
  • the plain bearing shell 100 has a generally semi-cylindrical geometry.
  • the plain bearing shell 100 includes two opposing axial ends 10, 10', an external surface 1 1 that is shaped to fit the piston 2, and an internal surface 12 opposite the external surface 1 1 . All or a portion of the internal surface 12 can be covered with, for example, an antifriction overlay/liner.
  • the internal surface 12 is adapted to support a roller or shaft 3 and allow the latter to rotate in the plain bearing shell 100 with a reduced coefficient of friction.
  • the plain bearing shell 100 is also provided with two opposing circumferential ends 13, 13'.
  • the two axial ends 10, 10' of the plain bearing shell 100 can be under-cut to form an elongated semi-circular shaped recess 14.
  • This recess 14 is configured to interact (e.g., mate) with a semi-circular concentric protrusion 16, 16' located at opposite ends of the recess formed in the piston 2, thereby preventing the rotation of the plain bearing shell 100 in either direction within the recess of piston 2 when a roller or shaft 3 is disposed in the piston 2 and rotating.
  • This anti-rotation function is assisted by the fact that the thickness of the plain bearing shell 100 (i.e., the distance between the internal surface 12 and the external surface 1 1 ) at point A is larger than its thickness at point B. If the plain bearing shell 100 is subjected to a rotating motion in the piston 2 via the rotation of the roller or shaft 3 in the piston 2, the axial ends 10, 10' (having an increased thickness at point A) will come into contact with the protrusions 16, 16' of the piston 2 and thereby stop any rotation of the plain bearing shell 100.
  • the plain bearing shell 100 is prevented from rotating in the piston 2 by virtue of axial ends 10, 10' forming two semi-cylindrical recess 14 that interact with corresponding protrusions 16, 16' of the piston 2.
  • This configuration helps to assure axial positioning of the plain bearing shell 100 in the piston 2, and helps to prevent axial movement of the plain bearing shell 100.
  • the plain bearing shell 100 is sized so that there is no contact between the angled ends of the roller or the shaft and the load area of the plain bearing shell 1 in order to satisfy tribological principles.
  • the usable length (L max ) in the load area of the plain bearing shell is determined by the formula:
  • L g is the total length of the roller or the shaft and r g is the value of the radius of the curved portion of the roller or shaft that extends between the outer diameter of the roller or the shaft and its end faces (see, e.g., r g as illustrated in Figure 2d). Lmax is also illustrated in Figure 1 d.
  • the plain bearing shell 100 further includes two plain thrust bearings 14, 14' extending from the axial ends 10, 10' in a radially inward direction.
  • the orientation of the thrust bearings 14, 14' can also be considered perpendicular to the axis of the plain bearing shell 100.
  • the thrust bearings 14, 14' help to ensure an axial plain bearing thrust function for the roller or the shaft. This prevents an increase of the coefficient of friction resulting from contact between the roller/shaft ends and the axial walls of the recess in the piston .
  • An antifriction overlay/liner present on some or all of the opposing side walls 15, 15' of the thrust bearings 14, 14' enables a low coefficient of friction between the plain bearing shell 1 and the roller or the shaft 3.
  • the shape and the section (width x height) of the thrust bearings 14, 14' can be defined by the factor PV (MPa x m/s) arising from the contact between the roller or shaft and the thrust bearings, wherein P (MPa) is the pressure of contact between the opposing parts, and V (m/s) is the circumferential speed of the roller or shaft at the contact point.
  • the size of the thrust bearings 14, 14' will be determined in order that the factor PV will remain acceptable for the chosen plain bearing material.
  • the width of the aforementioned thrust bearings 14, 14' must be less than the width of side slots 17, 17' formed in the axial ends of the recess of the piston 2 in order not to interfere with the bearing assembly and not to influence the anti-rotation function of the plain bearing.
  • the protrusions 15, 15' may be configured to accommodate a plain bearing shell 100 having thrust bearings 14, 14'.
  • the protrusions 15, 15' will each include two separate protruding segments that engage with the recess 14 but which also permit the thrust bearings 14, 14' to be positioned between the two separate protruding segments of the protrusion 16, 16'.
  • the plain bearing shell 200 has a generally semi-cylindrical geometry.
  • the plain bearing shell 200 includes two opposing axial ends 20, 20', an external surface 21 shaped to fit with a piston, and an internal surface 22 opposite the external surface 21 .
  • the internal surface 22 may be fully or partially covered with an antifriction overlay/liner.
  • the plain bearing shell 200 is also provided with two opposing circumferential ends 23, 23'.
  • the two circumferential ends 23, 23' include two semi-cut tabs 24, 24' issued from the face 22 and protruding radially outwardly. These tabs 24, 24' are accommodated in a female imprint of the piston 2, which thereby prevents plain bearing shell 200 from rotating when the roller or the shaft turns in one or the other direction.
  • plain bearing shell 200 can be characterized by the fact that the two tabs 24, 24' form two parallel edges 25, 25' perpendicular to the axis of the roller or shaft and which fit against female imprint 20, 20' of the piston. This helps to assure that the axial positioning of the plain bearing shell 200 within the piston and prevents axial movement of the plain bearing shell 200.
  • the plain bearing shell 200 can further include two plain thrust bearings 26, 26' issued from ends 20, 20'.
  • the thrust bearings 26, 26' can be oriented perpendicular to the axis of the plain bearing shell 200 in order to assure an axial plain bearing thrust function for the roller or the shaft, preventing an increase of the coefficient of friction with a direct contact of roller/shaft ends to piston faces, and to allow a low coefficient of friction of the roller/shaft thanks the two plain thrust bearing faces 27, 27'.
  • the shape and the section (width x height) of the thrust bearings 26, 26' can be defined by the factor PV (MPa x m/s) arising from the contact between the roller or shaft and the thrust bearings, wherein P (MPa) is the pressure of contact between the opposing parts, and V (m/s) is the circumferential speed of the roller or shaft at the contact point.
  • the size of the thrust bearings will be determined in order that the factor PV will remain acceptable for the chosen plain bearing material.
  • the width of the aforementioned thrust bearings must be less than the width of the side slots of the piston 28, 28' in order not to interfere with the bearing assembly and not to influence the anti-rotation function of the plain bearing.
  • the plain bearing shell 200 can be sized so that there is no contact between the angled ends of the roller or the shaft and the load area of the plain bearing shell 200 in order to satisfy tribological principles.
  • the usable length in the load area is determined by the formula:
  • L max L g - (2 x r g ) [0038] wherein L g is total length of the roller or the shaft and r g is the value of the radius of the curved portion of the roller or shaft that extends between the outer diameter of the roller or the shaft and its end faces. L max is also illustrated in Figure 2d.
  • the two plain thrust bearings 26, 26' can be linked to the ends 20, 20' of the plain bearing shell 100 by ties 28, 28'. These ties 28, 28' may be tilted at an angle, such as in a radially outward direction. In some embodiments, the ties are angled outwardly such that the plain thrust bearings 26, 26' extend beyond the circumference of the plain bearing shell 200. This can help to ensure no contact between the roller or the shaft in this area and thus satisfy the tribological principles described above.
  • a semi- cylindrical plain bearing shell 300 is secured to the piston 2 via welded spots or beads 37, 37' to thereby prevent rotation of the plain bearing shell.
  • the welded spots 37, 37' may be located between the piston 2 and the portion of external surface 32 proximate the circumferential ends 33, 33'.
  • the welded spots 37. 37' may be located in the countersunk areas of the piston recess.
  • a plain bearing shell 400 is described wherein the plain bearing shell 400 extends more than 180 degrees in the circumferential direction.
  • This plain bearing shell 400 may also be described as having a distance between circumferential ends 43, 43' that is less than the diameter of the roller or shaft 3 disposed therein.
  • the roller or shaft is disposed in the plain bearing shell by sliding the roller of shaft in from either axial end of the plain bearing shell.
  • the sub assembly of the plain bearing shell and the roller or shaft is then disposed in the piston recess.
  • the sub-assembly is spot welded to the piston in order to prevent rotation of the plain bearing shell. Once constructed in this manner, the full assembly provides the benefit of being made from three indissociable components.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Pistons, Piston Rings, And Cylinders (AREA)

Abstract

La présente invention concerne des enveloppes de palier lisse comprenant des éléments anti-rotation. Dans certains modes de réalisation, une enveloppe de palier lisse de forme semi-cylindrique comprend une cavité à chaque extrémité axiale de l'enveloppe. Des saillies comprises dans la cavité de piston dans laquelle l'enveloppe de palier lisse est disposée sont en prise avec les cavités et empêchent toute rotation de l'enveloppe de palier lisse. Dans certains modes de réalisation, une enveloppe de palier lisse de forme semi-cylindrique comprend une languette dépassant radialement vers l'extérieur à chaque extrémité circonférentielle de l'enveloppe. Une empreinte femelle comprise dans la cavité de piston dans laquelle est disposée l'enveloppe de palier lisse reçoit les languettes, empêchant ainsi toute rotation de l'enveloppe de palier lisse.
PCT/US2016/065803 2015-12-09 2016-12-09 Enveloppe de palier lisse dotée d'éléments anti-rotation Ceased WO2017100555A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US201562264994P 2015-12-09 2015-12-09
US62/264,994 2015-12-09

Publications (1)

Publication Number Publication Date
WO2017100555A1 true WO2017100555A1 (fr) 2017-06-15

Family

ID=59013582

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/US2016/065803 Ceased WO2017100555A1 (fr) 2015-12-09 2016-12-09 Enveloppe de palier lisse dotée d'éléments anti-rotation

Country Status (1)

Country Link
WO (1) WO2017100555A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102021124659B4 (de) 2020-09-28 2022-12-29 Daido Metal Company Ltd. Lagervorrichtung in Form eines Halblagers für die zylindrische Rolle des Kolbens einer Radialkolbenmaschine
US12018566B2 (en) 2020-09-28 2024-06-25 Daido Metal Company Ltd. Bearing device for radial piston machine

Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3926185A1 (de) * 1989-08-08 1991-02-14 Rexroth Mannesmann Gmbh Lagerschale fuer radialkolbenmaschine
JP2003239938A (ja) * 2002-02-20 2003-08-27 Honda Motor Co Ltd 軸受構造
US20090165641A1 (en) * 2006-03-31 2009-07-02 Gilles Lemaire Piston for a hydraulic motor having radial pistons, and a method of manufacturing such a piston
US20090183629A1 (en) * 2006-04-05 2009-07-23 Gilles Lemaire Piston for radial piston hydraulic engine and method for making same
US20120027328A1 (en) * 2010-07-30 2012-02-02 Daodo Metal Company Ltd. Manufacturing method of half bearing and half plain bearing
EP2466119A1 (fr) * 2010-12-18 2012-06-20 KS Gleitlager GmbH Piston pour machine à piston radial
US8251590B2 (en) * 2009-05-29 2012-08-28 Cummins Intellectual Properties, Inc. Anti-rotation bearing assembly and bearing
US20130004103A1 (en) * 2011-06-30 2013-01-03 Caterpillar, Inc. Sleeve Bearing with Shell Portions of Unequal Extent
US8511900B2 (en) * 2010-03-19 2013-08-20 Federal-Mogul Wiesbaden Gmbh Sliding bearing shell
WO2015128362A1 (fr) * 2014-02-27 2015-09-03 Ks Gleitlager Gmbh Coquille de coussinet lisse et piston pour moteur à pistons radiaux
WO2016097230A1 (fr) * 2014-12-17 2016-06-23 Poclain Hydraulics Industrie Piston à galet monobloc et procédé associé

Patent Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3926185A1 (de) * 1989-08-08 1991-02-14 Rexroth Mannesmann Gmbh Lagerschale fuer radialkolbenmaschine
JP2003239938A (ja) * 2002-02-20 2003-08-27 Honda Motor Co Ltd 軸受構造
US20090165641A1 (en) * 2006-03-31 2009-07-02 Gilles Lemaire Piston for a hydraulic motor having radial pistons, and a method of manufacturing such a piston
US20090183629A1 (en) * 2006-04-05 2009-07-23 Gilles Lemaire Piston for radial piston hydraulic engine and method for making same
US8251590B2 (en) * 2009-05-29 2012-08-28 Cummins Intellectual Properties, Inc. Anti-rotation bearing assembly and bearing
US8511900B2 (en) * 2010-03-19 2013-08-20 Federal-Mogul Wiesbaden Gmbh Sliding bearing shell
US20120027328A1 (en) * 2010-07-30 2012-02-02 Daodo Metal Company Ltd. Manufacturing method of half bearing and half plain bearing
EP2466119A1 (fr) * 2010-12-18 2012-06-20 KS Gleitlager GmbH Piston pour machine à piston radial
US20130004103A1 (en) * 2011-06-30 2013-01-03 Caterpillar, Inc. Sleeve Bearing with Shell Portions of Unequal Extent
WO2015128362A1 (fr) * 2014-02-27 2015-09-03 Ks Gleitlager Gmbh Coquille de coussinet lisse et piston pour moteur à pistons radiaux
WO2016097230A1 (fr) * 2014-12-17 2016-06-23 Poclain Hydraulics Industrie Piston à galet monobloc et procédé associé

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102021124659B4 (de) 2020-09-28 2022-12-29 Daido Metal Company Ltd. Lagervorrichtung in Form eines Halblagers für die zylindrische Rolle des Kolbens einer Radialkolbenmaschine
US12018566B2 (en) 2020-09-28 2024-06-25 Daido Metal Company Ltd. Bearing device for radial piston machine
US12065933B2 (en) 2020-09-28 2024-08-20 Daido Metal Company Ltd. Bearing device for radial piston machine

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