EP1893878A2 - Systeme de coquille de coussinet, coussinet et demi-coquille de coussinet demi-circulaire - Google Patents

Systeme de coquille de coussinet, coussinet et demi-coquille de coussinet demi-circulaire

Info

Publication number
EP1893878A2
EP1893878A2 EP06762158A EP06762158A EP1893878A2 EP 1893878 A2 EP1893878 A2 EP 1893878A2 EP 06762158 A EP06762158 A EP 06762158A EP 06762158 A EP06762158 A EP 06762158A EP 1893878 A2 EP1893878 A2 EP 1893878A2
Authority
EP
European Patent Office
Prior art keywords
bearing
shell
bearing shell
halves
width
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Withdrawn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
EP06762158A
Other languages
German (de)
English (en)
Inventor
Martin Klein
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.)
Federal Mogul Wiesbaden GmbH
Original Assignee
Federal Mogul Wiesbaden 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 Federal Mogul Wiesbaden GmbH filed Critical Federal Mogul Wiesbaden GmbH
Publication of EP1893878A2 publication Critical patent/EP1893878A2/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Withdrawn legal-status Critical Current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
    • 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
    • F16C17/10—Sliding-contact bearings for exclusively rotary movement for both radial and axial load
    • 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
    • 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
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/66—Special parts or details in view of 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
    • F16C35/00—Rigid support of bearing units; Housings, e.g. caps, covers
    • 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

Definitions

  • the invention relates to a bearing shell assembly, a bearing and a semi-circular bearing shell half.
  • the invention relates to a crankshaft main bearing and a mass balance gearbox bearing.
  • the crankshaft of motor vehicle or truck engines is stored in so-called main bearings, via which the oil supply of the connecting rod bearing of the crankshaft takes place.
  • the main bearings are designed with and without collar.
  • the main bearing has an upper bearing shell, which has at least one oil hole and an oil groove extending substantially over the entire inner circumference.
  • the corresponding crankshaft journal has a radial oil bore, through which the oil provided in the upper bearing shell is removed and fed to the connecting rod bearing.
  • the upper bearing shell is designed with and without collar.
  • Such flange bearing shells are known for example from US 4,845,817. As a rule, however, they are so-called built-up flange bearing shells, in which the thrust washers are arranged movably on the bearing shell. Bearing shells with and without collar and with oil groove are also used in so-called mass balancing gearbox bearings.
  • the requirements for such bearings relate, inter alia, the size of the flow cross-section of the oil groove.
  • a wide and deep oil groove is desirable.
  • the depth in terms of stability of the bearing shell limits. Due to the small material thickness at the groove bottom, the bearing shell back may not be completely in the bearing seat. If the oil grooves are too wide, the remaining bearing area of the bearing shell is again too small.
  • Another disadvantage of the conventional bearing shells is that the oil groove must be made by a machining operation, that at least one oil hole must be introduced and that the removed material must be disposed of as waste. During the production of the oil groove as well as during the production of the oil well smallest chips (baubles) are created. These are extremely disturbing in the manufacturing process and must be eliminated by expensive washing operations.
  • the invention preferably relates to bearing shells having an outer diameter of 20 mm to 150 mm.
  • the width Bi of the bearing cup assembly includes the widths of the two bearing shell halves and the width of the oil channel formed between the bearing shell halves. This width Bi is predetermined by the width B 3 of the bearing cup receptacle or bearing bore in the bearing housing. In the case of bearing shell halves with axial bearing parts attached to the edge, the bearing shell halves protrude opposite the bearing bore, so that B 3 ⁇ Bi. In general, B 3 ⁇ B 1 .
  • an oil passage is formed, for the depth according to the invention, the entire thickness of the bearing shell is available. If the widths B 2 of the two bearing shell halves corresponds to the width of the wing portion of conventional individual bearing shells with an oil groove, the oil passage has a larger flow cross-section than the oil groove in the conventional bearing shell. Conversely, with the same flow cross-section as in conventional bearing shells, the wing portion can be increased by a correspondingly greater width of the bearing shell half.
  • the width of the oil passage and thus the flow cross section can be selected by the user himself by determining the distance of the bearing shell halves by the choice of the width B 2 to each other.
  • Each bearing shell half preferably has an axial bearing part at each edge. While in conventional flange bearing shells the impbundment between the two Axiallager sculpture is fixed, this can now be chosen freely. The bearing shell halves are thus used variably.
  • both bearing shell halves are identical.
  • the production can be considerably simplified.
  • the oil passage extends over the entire circumferential length of the bearing shell halves.
  • the two bearing shell halves do not touch.
  • a particular use of at least two semicircular bearing shell halves is provided for oil-lubricated bearings, especially in vehicle engines.
  • the oil-lubricated bearing having a first and a second bearing shell, which abut each other at their partial surfaces, is characterized in that at least one of the two bearing shells is divided into two and consists of two semicircular bearing shell halves, which are arranged in the axial direction of the bearing spaced from each other, wherein between the Bearing shell halves a circumferentially extending oil passage is formed.
  • the crankshaft main bearing with a bearing housing having a bearing bore of width B 3 and a bearing arrangement of the width Bi used in the bearing housing of an upper shell and a lower shell, wherein the bearing housing has at least one oil supply to the upper shell, characterized in that the upper shell is divided into two parts and two semicircular bearing shell halves is arranged, which are arranged spaced from each other in the axial direction of the bearing, wherein between the bearing shell halves, a circumferentially extending oil passage is formed, in which the oil supply opens.
  • the mass balancing transmission bearing with a bearing housing having a bearing bore of width B 3 and an upper shell inserted in the bearing housing and a lower shell, wherein the bearing housing has at least one oil supply to the lower shell, characterized in that the lower shell is divided into two and consists of two semicircular bearing shell halves , which are spaced apart in the axial direction of the bearing, wherein between the bearing shell halves, a circumferentially extending oil passage is formed, in which the oil supply opens.
  • the bearing shell halves of the crankshaft main bearing and the mass balance gear bearing can be provided with or without thrust bearing parts.
  • a semi-circular bearing shell half width B 2 with outer diameter D and partial surfaces is characterized in that the bearing shell half with a second half-circular bearing shell half width B 2 to a bearing shell arrangement of the width Bi for a bearing is assembled, the two bearing shell halves in the axial direction next to each other are arranged, which is located between the bearing shell halves extending in the circumferential direction of the bearing shell halves oil passage, and that for the ratio V of bearing shell outer diameter D in mm to width B 2 in mm of the bearing shell half applies: 2.5 ⁇ V ⁇ 6 for 20 ⁇ D ⁇ 24 2.4 ⁇ V ⁇ 10 for 24 ⁇ D ⁇ 40
  • the semi-circular bearing shell half has at least one retaining cam in the partial surface, which projects from the outer circumference of the bearing shell half.
  • a retaining cam is provided in each partial area. The provision of at least one retaining cam in each partial area has the advantage that a high level of alignment accuracy is ensured and an axial wandering in the bearing seat is prevented.
  • the semi-circular bearing shell half is characterized by an axial bearing part which is arranged on an edge of the bearing shell half.
  • the bearing shell halves are characterized by a lesser skew of the partial surfaces ( ⁇ 0.03 mm) with respect to the apex area.
  • FIG. 2 a perspective view of a bearing according to a further embodiment, 3 shows a section through the bearing assembly of Figure 2 in the installed state, and
  • FIG. 4 shows a bearing shell half according to a further embodiment.
  • FIG. 1 shows a bearing 1 with an upper shell 4 and a lower shell 3. While the lower shell 3 is a one-piece smooth shell, the upper shell 4 is divided into two and consists of a bearing shell assembly 10 of width B 1 with two semicircular bearing shell halves 11 of width B 2 , which are spaced from each other, so that between the two bearing shell halves 11, a gap 12th is formed, which forms an oil passage 14 in the installed state together with the bearing housing. This will be explained in connection with FIG.
  • the bearing shell assembly 10 is formed from two mutually spaced bearing shell halves 11 ', each having an axial bearing 13 at its outer edge.
  • Such bearings are used inter alia as a crankshaft main bearing 2.
  • the lower shell 3 consists of a one-piece smooth shell.
  • FIG. 3 shows a partial section through the bearing 1 shown in FIG. 2, the section extending through the bearing shell arrangement 10.
  • the bearing housing 20 is located, which has an oil feed 21 in the center. This oil supply 21 opens into the intermediate space 12 between the two bearing shell halves 11 ', which thus forms an oil passage 14.
  • the entire bearing shell thickness LD is available for the oil passage 14.
  • FIG. 3 is representative of a crankshaft main bearing 2, wherein the bearing housing 20 is formed by a connecting rod.
  • the bearing receptacle 22 is in this example the large connecting rod eye.
  • Figure 3 is also representative of a
  • Mass balance gear bearing in which case the lower shell is formed by two axially adjacent bearing shell halves.
  • FIG. 4 shows a perspective view of a bearing shell half with an axial bearing part 13.
  • Each partial surface 16 of the semicircular bearing shell half 11 ' has a retaining cam 15, which protrudes with respect to the outer peripheral surface.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)
  • Sliding-Contact Bearings (AREA)

Abstract

L'invention concerne un système de coquille de coussinet (10) de largeur B1 destiné à un coussinet (1). Ce système comprend deux demi-coquilles de coussinet (11, 11') demi-circulaires espacées dans le sens axial, chaque demi-coquille présentant une largeur B2 < B1/2. Une rainure de graissage (14) s'étendant dans le sens circonférentiel des demi-coquilles de coussinet (11, 11') est située entre lesdites demi-coquilles de coussinet (11, 11').
EP06762158A 2005-06-23 2006-06-23 Systeme de coquille de coussinet, coussinet et demi-coquille de coussinet demi-circulaire Withdrawn EP1893878A2 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102005030307.2A DE102005030307B4 (de) 2005-06-23 2005-06-23 Kurbelwellenhauptlager und Massenausgleichsgetriebelager
PCT/EP2006/006061 WO2006136432A2 (fr) 2005-06-23 2006-06-23 Systeme de coquille de coussinet, coussinet et demi-coquille de coussinet demi-circulaire

Publications (1)

Publication Number Publication Date
EP1893878A2 true EP1893878A2 (fr) 2008-03-05

Family

ID=37003294

Family Applications (1)

Application Number Title Priority Date Filing Date
EP06762158A Withdrawn EP1893878A2 (fr) 2005-06-23 2006-06-23 Systeme de coquille de coussinet, coussinet et demi-coquille de coussinet demi-circulaire

Country Status (7)

Country Link
US (1) US20090226123A1 (fr)
EP (1) EP1893878A2 (fr)
JP (1) JP2008544188A (fr)
KR (1) KR20080022112A (fr)
BR (1) BRPI0612304A2 (fr)
DE (1) DE102005030307B4 (fr)
WO (1) WO2006136432A2 (fr)

Families Citing this family (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102007044250B4 (de) 2007-09-11 2012-04-19 Federal-Mogul Wiesbaden Gmbh Gleitlagerschale, Verwendung der Gleitlagerschale, Verfahren zu ihrer Herstellung und Lageranordnung
JP5141339B2 (ja) * 2008-03-31 2013-02-13 オイレス工業株式会社 ブッシュ軸受及びそれを用いた自動車のラック−ピニオン式操舵装置
GB201103261D0 (en) * 2011-02-25 2011-04-13 Mahle Int Gmbh A bearing arrangement
DE102011005466B9 (de) 2011-03-11 2012-12-06 Federal-Mogul Wiesbaden Gmbh Gleitlagerschale
CN103775500B (zh) * 2014-01-21 2016-03-09 芜湖美达机电实业有限公司 一种厚壁轴瓦
JP6507695B2 (ja) 2015-02-10 2019-05-08 スズキ株式会社 内燃機関のオイル供給構造
WO2016201598A1 (fr) * 2015-06-15 2016-12-22 钱国庆 Coussinet de palier pour moteur d'automobile
CN105057710B (zh) * 2015-07-17 2017-06-30 安阳工学院 电主轴的均压气封和针孔内伸式润滑的装置
DE102016220595A1 (de) * 2016-10-20 2018-04-26 Robert Bosch Gmbh Lagerbuchse, insbesondere Gleitlagerbuchse
CN108730342A (zh) * 2017-04-15 2018-11-02 广西隆盛双金属铜合金制造有限公司 大型轴瓦及其压铸方法

Citations (2)

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DE3621577A1 (de) * 1985-07-26 1987-02-05 Glyco Metall Werke Gleitlager
JPS63115628A (ja) * 1986-10-31 1988-05-20 Sumitomo Metal Ind Ltd 電磁成型器

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GB607400A (en) * 1946-02-01 1948-08-30 Hoyt Metal Company Of Great Br Improvements in bearings
US2673767A (en) * 1950-08-16 1954-03-30 Harnischfeger Corp Sleeve bearing
US2678767A (en) 1950-10-24 1954-05-18 Bartgis Brothers Company Carton for like articles
DE1872947U (de) * 1961-05-05 1963-05-30 Kloeckner Humboldt Deutz Ag Lagerschale.
CS165298B1 (fr) * 1973-11-08 1975-12-22
DE2433929A1 (de) * 1974-07-15 1976-02-05 Glyco Metall Werke Kombiniertes radial-axial-gleitlager
US4073550A (en) * 1976-05-26 1978-02-14 Gould Inc. Sleeve bearing
US4168636A (en) * 1977-09-09 1979-09-25 Vilter Manufacturing Corporation Refrigeration compressor having multi-part crankshaft
SU1446375A1 (ru) * 1987-04-13 1988-12-23 Производственное объединение "Волгодизельмаш" Вкладыш подшипника скольжени высокофорсированного дизел
US4845817A (en) * 1988-06-29 1989-07-11 J. P. Industries, Inc. Method of forming a half-round bearing
DE19710590A1 (de) * 1997-03-14 1998-11-12 Josif Velkovski Exploatation Öldruckes im Automotor (Diesel und Benziner)
JP2000179535A (ja) * 1998-12-16 2000-06-27 Honda Motor Co Ltd 分割型コンロッドにおける軸受メタルの位置決め構造
BR0114340B1 (pt) * 2000-09-29 2009-08-11 mancal de colar soldado, processo para a fabricação de mancais de colar soldados e dispositivo para a execução do processo.
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JPS63115628A (ja) * 1986-10-31 1988-05-20 Sumitomo Metal Ind Ltd 電磁成型器

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Title
See also references of WO2006136432A2 *

Also Published As

Publication number Publication date
BRPI0612304A2 (pt) 2010-11-03
JP2008544188A (ja) 2008-12-04
WO2006136432A2 (fr) 2006-12-28
KR20080022112A (ko) 2008-03-10
WO2006136432A3 (fr) 2007-04-26
DE102005030307A1 (de) 2006-12-28
US20090226123A1 (en) 2009-09-10
DE102005030307B4 (de) 2014-02-13

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