EP2978982A2 - Surface coulissante - Google Patents

Surface coulissante

Info

Publication number
EP2978982A2
EP2978982A2 EP14711511.7A EP14711511A EP2978982A2 EP 2978982 A2 EP2978982 A2 EP 2978982A2 EP 14711511 A EP14711511 A EP 14711511A EP 2978982 A2 EP2978982 A2 EP 2978982A2
Authority
EP
European Patent Office
Prior art keywords
sliding surface
better
recesses
μιτι
area
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.)
Withdrawn
Application number
EP14711511.7A
Other languages
German (de)
English (en)
Inventor
Leo Schreiber
Jürgen REINGEN
Matthias Weber
Wolfgang Hafner
Emanuel GROß
Andreas Grützmacher
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.)
MAG IAS GmbH Eislingen
Original Assignee
MAG IAS GmbH Eislingen
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 MAG IAS GmbH Eislingen filed Critical MAG IAS GmbH Eislingen
Priority to EP14711511.7A priority Critical patent/EP2978982A2/fr
Publication of EP2978982A2 publication Critical patent/EP2978982A2/fr
Withdrawn legal-status Critical Current

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
    • 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
    • F16C3/00—Shafts; Axles; Cranks; Eccentrics
    • F16C3/04—Crankshafts, eccentric-shafts; Cranks, eccentrics
    • F16C3/06—Crankshafts
    • F16C3/08—Crankshafts made in one piece
    • 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
    • F16C3/00—Shafts; Axles; Cranks; Eccentrics
    • F16C3/04—Crankshafts, eccentric-shafts; Cranks, eccentrics
    • F16C3/06—Crankshafts
    • F16C3/14—Features relating to lubrication
    • 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
    • F16C33/103—Construction relative to lubrication with liquid, e.g. oil, as lubricant retained in or near 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
    • 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
    • F16C33/107—Grooves 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
    • F16C9/00—Bearings for crankshafts or connecting-rods; Attachment of connecting-rods
    • F16C9/02—Crankshaft bearings
    • 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
    • F16C9/00—Bearings for crankshafts or connecting-rods; Attachment of connecting-rods
    • F16C9/04—Connecting-rod bearings; Attachments thereof
    • 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
    • F16C2240/40—Linear dimensions, e.g. length, radius, thickness, gap
    • F16C2240/42—Groove sizes
    • 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
    • F16C2240/40—Linear dimensions, e.g. length, radius, thickness, gap
    • F16C2240/44—Hole or pocket sizes
    • 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
    • F16C2360/22—Internal combustion engines

Definitions

  • the invention relates to a sliding surface of a sliding pair, in particular the plain bearing surface of a radial bearing, in particular the bearing points of a crankshaft in an internal combustion engine, on the one hand with respect to the engine block and on the other hand with respect to the connecting rods.
  • the contact surfaces of sliding surfaces are processed so that they have very small depressions with a depth of well below 100 ⁇ , which serves as a reservoir for lubricants. tel serve. These recesses are present due to the normal roughness of the material of the sliding surface, or are deliberately introduced. Because of this, the bearing portion of a plain bearing, ie the area proportion with which the contact surfaces actually abut one another, is always clearly below 100%, sometimes even below 60%.
  • the corresponding structuring of the sliding surfaces is achieved by special processing steps such as grinding, finishing or honing, in which, however, the concrete shape and distribution of the depressions can not be specified, and also the variation in size, in particular the depth, of these depressions is relatively large. Above all, the result of the structuring also depends heavily on the experience of the executing person. In order to achieve a structuring of the contact surface of a slide bearing defined with regard to number, size, depth and distribution of the depressions, it is likewise already known to bombard this surface by means of a laser and thereby achieve the desired depressions.
  • a further disadvantage is that the laser processing results in a spatially limited, strong heating and subsequent rapid cooling, which leads to unwanted new hardness zones.
  • ECM electrochemical erosion
  • PECM pulsed mode
  • an electrically conductive liquid is pressed through the gap between the tool and the workpiece during the entire process.
  • crankshafts as workpieces
  • crankshafts for passenger car engines with high numbers of cylinders it is added that during machining they are unstable and thus difficult to position and also difficult to machine during structuring workpieces.
  • Roundness macroscopic deviation from the circular nominal contour of the bearing journal, indicated by the distance of the outer and inner enveloping circle,
  • Supporting component the bearing surface portion of the microscopically considered surface structure, which is in contact with an adjacent mating surface
  • Stroke deviation dimensional deviation of the actual stroke (distance of the actual center of the crankpin from the actual center of the center bearing), the desired stroke and
  • Angular deviation in degrees or as a stroke-related measure of length in the circumferential direction specified deviation of the actual angular position of the pin bearing pin from its desired angular position relative to the center bearing axis and with respect to the angular position to the other lifting bearing pin.
  • a meaningful upper limit has been found for the smallest extent of a depression considered in the order, namely a maximum of 150 ⁇ , better 100 ⁇ , better at most 50 ⁇ .
  • the maximum extent of the depression should be at most a factor of 10, better at most only by a factor of 5, better at most only by a factor of 3 as large as the smallest extent of the depression.
  • the depth of the wells should be at least 1%, better at least 5%, better at least 20%, better at least 40%, better at least 50% of this largest extension.
  • the smallest distance between two adjacent depressions is at least twice, better at least three times, better at least five times the considered in the supervision largest extension of the two wells involved and at most seven times, better than that ten times, the largest extension of the two recesses considered in the supervision.
  • angle to the surface should not be greater than 80 °, better 45 °, better than 30 °, better than 25 °, but at the same time this angle should be at least 45 °, preferably at least 60 °
  • the sliding bearing surface should be structured differently in these areas, even if the sliding surface anyway Only in part, namely in the more heavily loaded area, is the structure structured:
  • the depressions should be at least a factor of 2, better by a factor of 3, better by at least a factor of 5, in the region of the highest stress than in the region of the lowest stress.
  • the depth of the recesses should be at most 0.5 times, better at most 0.33 times, better at most only 0.1 times the bearing gap.
  • the maximum extent of the depressions considered in the plan view should be at most 14 times, better at most 8 times, better at most 4 times the radial extent of the mechanical bearing gap.
  • FIG. 1 shows a crankshaft for a 4-cylinder internal combustion engine in the side view
  • Figure 2a the crankshaft of Figure 1 in the axial direction, cut through one of the center bearings
  • FIG. 2b a crankshaft for a 6-cylinder internal combustion engine viewed in the axial direction and cut through a center bearing
  • FIG. 3a a plan view of a structured region of a sliding surface, the enlarged view of a bearing point of a crankshaft
  • Figure 3c another enlarged view of a bearing of a
  • Figure 4a, b sections through depressions in the sliding surface.
  • Figure 1 shows a typical workpiece on which sliding surfaces 1 are to be structured for reducing friction by means of depressions, a crankshaft 2 for a 4-cylinder reciprocating engine in the side view, in which on the later axis of rotation 10 of the crankshaft a total of five center bearings 1b with their approximately cylindrical Jacket surfaces are available as sliding surfaces 1. Between each of these center bearing points 1b, each offset radially outwardly, depending on one of four Hublagerstellen 1a, which also each have an approximately cylindrical bearing surface as sliding surface 1 for each associated connecting rod, and are connected to the center bearings 1b cheeks 5.
  • crankshaft 2 only one subregion 11 of a bearing 1 a, 1 b of the crankshaft 2 is structured, in the circumferential direction of the bearing points as shown in FIGS. 2 a and b:
  • FIGS. 2 a and b For the illustrated crankshafts for a four-cylinder (FIG. 2 a) or one Six-cylinder reciprocating engine (Fig. 2b) takes place during operation, the largest load on the crankpins 1a at the time of ignition of the gas mixture and in the short time thereafter, in which the explosion pressure builds up in the cylinder and accelerates the piston down.
  • the connecting rod presses on the peripheral region 11a1 of the currently located overhead bearing 1a, the center of which is located in the direction of rotation 28 of the crankshaft 2 behind the point 13 of the crankcaster journal 1a radially farthest from the axis of rotation 10 of the crankshaft. Since the bearing shell of the connecting rod is not supported at points, but over a certain peripheral area on the journal, the most heavily loaded peripheral area shark - depending on how generous you interpret it - an area that may even be just before the radially outermost Point 13 begins and extends over an angular segment opposite to the direction of rotation 28 of eg 60 °.
  • crankpin 1a this is the analogue area when it is in the highest position.
  • the pressure exerted by the connecting rod transmits primarily to the corresponding crankpin, but from there via the cheeks 5 at least to the two axially adjacent center bearing pin 1b and less strongly on the axially farther centering journal 1 b, the through the pressure of the connecting rod on the side opposite the circumferential area Hai with the peripheral area Hai 'are pressed into its bearing shell. Therefore, the two circumferential portions 11a1 and 11a2 diametrically opposite circumferential regions Hai ', Ha2' of the center bearing journal 1b are also heavily loaded areas.
  • the heavily loaded peripheral regions 11a are exclusively structured or structured more strongly than the rest of the storage location, but preferably only these regions are structured, in order to be able to save processing of the remaining regions.
  • FIG. 3b furthermore shows that only the middle width region 11b of the bearing 1 is structured transversely to the direction of movement 28 of the circumferential direction, that is to say in the axial direction 10.
  • either the entire width of the bearing point 1 or only the axially middle region of the bearing point 1 is structured according to the invention in the axial direction, possibly also in addition to the structuring, which may also be only zone-wise in the circumferential direction.
  • the sliding surface is provided in the structured region with a multiplicity of very small depressions 27, as shown in the enlarged plan view of FIG. 3a, since it has been found that even a structurally structuring considerably reduces the friction:
  • recesses 27 are viewed in plan view, for example, round or elongated designed, for example in the form of a short groove with semicircular ends with a smallest extension e and a maximum Er- stretch E and a mutual minimum distance 21, as shown in Figure 3a.
  • the surface portion of the depressions 27 within the structured region 11 should be in the range of 15% to 40% of the total area of the structured region 11.
  • the distance 21 from center to center between two adjacent recesses 27 should be at least three times, better at least five times, better at least seven times the considered in the supervision of the largest extension E of the depression amount.
  • the recesses 27 are preferably arranged in a uniform grid, for example a diamond-shaped grid, whose one diagonal lies in the circumferential direction 28.
  • elongated recesses 27 their main extension direction 20 should lie primarily in the circumferential direction 28 of the bearing 1, that is to say the later direction of rotation, and for this purpose assume an angle of not more than 30 °.
  • the recesses 27 should also not be stretched too long, namely the maximum extent E a maximum of ten times, better only a maximum of three times as large as the smallest extension e, which is also shown in Figure 3a.
  • FIG. 3c shows, in the structured region an optimum ratio of benefit to expense can be achieved by a variation of the sizes and distances of the depressions 27 within the structured region:
  • the depressions 27 are the smallest and have the smallest distance 21 from one another.
  • the recesses 27 in the plan view are much larger, but their distance also larger, so that either by appropriate determination of the distance of the same or a slightly smaller area proportion of the structured surface with depressions 27 is busy.
  • the third, even less loaded, even further away from the line of symmetry area is equipped with even larger recesses 27, which have for example three times the diameter compared to the first area, while the diameter in the second region is twice the diameter.
  • the area fraction occupied by the structured area with recesses 27 can be be the same or lower than in the first and second ranges.
  • the recesses 27 may have a smallest extension e, for example in the case of round recesses 27 having a diameter d of not more than 150 or even only 50 ⁇ .
  • FIGS. 4a, b show the shape of the flanks 18 of the depressions 27:
  • the depressions symmetrically, in particular rotationally symmetric, be designed so the flanks 18 have the same angle of inclination 9 to the surface of the bearing 1.
  • the flank 18 should transition into the surface of the bearing 1 with a rounding 8 of at least a radius of 2 ⁇ , as shown in Figure 4a on the left flank. Both measures contribute to the fact that the lubricant absorbed in the recesses 27 during operation of the crankshaft can be well transported away in the circumferential direction 28 by means of adhesion to the contact surface of the bearing block, ie the mating surface 20 to the sliding surface 1 and thus into the bearing gap 3 away from the Recesses 27 can be transported into it.
  • the bearing gap 3 should be less than the depth t of the recesses 27, preferably less than 0.5 times their depth.
  • These areas between the recesses should also have a sufficient support content of, for example, 60% to 70%.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Oil, Petroleum & Natural Gas (AREA)
  • Ocean & Marine Engineering (AREA)
  • Sliding-Contact Bearings (AREA)
  • Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)
  • Manufacture Of Macromolecular Shaped Articles (AREA)
  • Treatments Of Macromolecular Shaped Articles (AREA)

Abstract

On connaît la structuration de surfaces de palier lisse (1) en y creusant des cavités de taille microscopique (27), notamment par mise en œuvre de processus électrochimiques d'enlèvement de mlatière. Selon l'invention, on réduit au sein de la surface ainsi structurée la proportion surfacique desdites cavités de manière à ce qu'elles ne représentent pas plus de 15 % à 40 % de la surface structurée prise dans sa totalité. Cela permet de simplifier le traitement, étant donné qu'une proportion plus élevée de cavités (27) ne permet guère d'obtenir une diminution plus importante de la friction dans le palier lisse.
EP14711511.7A 2013-03-25 2014-03-20 Surface coulissante Withdrawn EP2978982A2 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP14711511.7A EP2978982A2 (fr) 2013-03-25 2014-03-20 Surface coulissante

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
EP13160919 2013-03-25
DE201310109043 DE102013109043A1 (de) 2013-03-25 2013-08-21 Gleitfläche
PCT/EP2014/055607 WO2014154561A2 (fr) 2013-03-25 2014-03-20 Surface coulissante
EP14711511.7A EP2978982A2 (fr) 2013-03-25 2014-03-20 Surface coulissante

Publications (1)

Publication Number Publication Date
EP2978982A2 true EP2978982A2 (fr) 2016-02-03

Family

ID=48082854

Family Applications (1)

Application Number Title Priority Date Filing Date
EP14711511.7A Withdrawn EP2978982A2 (fr) 2013-03-25 2014-03-20 Surface coulissante

Country Status (10)

Country Link
US (1) US20160146251A1 (fr)
EP (1) EP2978982A2 (fr)
JP (1) JP2016514806A (fr)
KR (1) KR20150132153A (fr)
CN (1) CN105051386A (fr)
BR (1) BR112015024704A2 (fr)
DE (1) DE102013109043A1 (fr)
MX (1) MX2015011106A (fr)
RU (1) RU2015141355A (fr)
WO (1) WO2014154561A2 (fr)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP6406372B2 (ja) * 2017-03-06 2018-10-17 マツダ株式会社 往復動ピストンエンジンおよびこれを備えた車両
KR102601952B1 (ko) * 2018-04-18 2023-11-14 가네후사 가부시키가이샤 딤플이 형성된 피가공물 및 딤플 가공 방법
EP3798456A1 (fr) * 2019-09-27 2021-03-31 Flender GmbH Palier lisse
DE102020102085A1 (de) 2020-01-29 2021-07-29 Audi Aktiengesellschaft Verfahren zum Herstellen einer Kurbelwellenanordnung sowie entsprechende Kurbelwellenanordnung
US11619255B1 (en) * 2022-03-18 2023-04-04 GM Global Technology Operations LLC System and method of making a crankshaft with alternate materials

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AT392522B (de) * 1986-03-22 1991-04-25 Glyco Metall Werke Gleitlagerelement mit inhomogener antifriktionsschicht
DE19700339C2 (de) * 1996-01-30 2001-06-13 Federal Mogul Wiesbaden Gmbh Haupt- oder Pleuellagerelement
AT409409B (de) * 1996-01-30 2002-08-26 Glyco Metall Werke Gleitlagerelement mit schmieröltaschen
JP2001124081A (ja) * 1999-10-26 2001-05-08 Citizen Watch Co Ltd すべり軸受材料
ATE280909T1 (de) * 2001-07-09 2004-11-15 Gehring Gmbh & Co Kg Werkstück mit einer tribologisch beanspruchbaren fläche und verfahren zur herstellung einer solchen fläche
DE10254368B3 (de) * 2002-11-21 2004-06-17 Daimlerchrysler Ag Geschmiertes Gleitsystem und Verfahren zur Verminderung der Reibung
US7270482B2 (en) * 2004-02-05 2007-09-18 Nissan Motor Co., Ltd. Sliding device
ATE402350T1 (de) * 2005-03-09 2008-08-15 Skf Ab Gleitlager mit unterschiedlichen hohlraumgruppierungen
JP2008095721A (ja) * 2006-10-06 2008-04-24 Nissan Motor Co Ltd 摺動部材
DE102006062687A1 (de) * 2006-10-30 2008-05-08 Daimler Ag Verfahren und Elektrode zur Herstellung einer im wesentlichen zylinderförmigen Lagerfläche einer radialen Wellenlagerung in elektrisch leitfähigem Material sowie Pleuel
DE102006051719A1 (de) * 2006-10-30 2008-05-08 Daimler Ag Verfahren zur Bearbeitung einer beschichteten Reibkontaktfläche aus elektrisch leitfähigem Material und Elektrode zur elektrochemischen Bearbeitung
DE102006060920A1 (de) 2006-12-20 2008-07-03 Daimler Ag Laserstrukturierte Zylinderlaufbuchse
AT506855B1 (de) * 2008-05-28 2010-02-15 Minebea Co Ltd Verfahren zur optimierung der anzahl von lagerstrukturen auf einer lageroberfläche eines fluiddynamischen gleitlagers
US8470160B2 (en) * 2009-09-28 2013-06-25 General Electric Company Methods, systems and apparatus relating to electrochemical machining
DE102009049323B4 (de) 2009-10-14 2011-11-10 Bayerische Motoren Werke Aktiengesellschaft Verbrennungsmotor mit einem Kurbelgehäuse sowie Verfahren zur Herstellung eines Kurbelgehäuses
WO2012060487A1 (fr) * 2010-11-03 2012-05-10 두산인프라코어 주식회사 Cylindre pourvu d'un profil irrégulier sur la surface d'une paroi interne

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Also Published As

Publication number Publication date
KR20150132153A (ko) 2015-11-25
JP2016514806A (ja) 2016-05-23
WO2014154561A3 (fr) 2015-07-23
WO2014154561A2 (fr) 2014-10-02
DE102013109043A1 (de) 2014-09-25
BR112015024704A2 (pt) 2017-07-18
MX2015011106A (es) 2015-10-26
RU2015141355A (ru) 2017-05-02
CN105051386A (zh) 2015-11-11
US20160146251A1 (en) 2016-05-26

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