USRE39377E1 - Sliding bearing - Google Patents

Sliding bearing Download PDF

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Publication number
USRE39377E1
USRE39377E1 US10/210,813 US21081396A USRE39377E US RE39377 E1 USRE39377 E1 US RE39377E1 US 21081396 A US21081396 A US 21081396A US RE39377 E USRE39377 E US RE39377E
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US
United States
Prior art keywords
sliding bearing
peak
valley
reference line
bearing according
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.)
Expired - Lifetime
Application number
US10/210,813
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English (en)
Inventor
Yoshio Kumada
Katsuyuki Hashizume
Soji Kamiya
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.)
Taiho Kogyo Co Ltd
Original Assignee
Taiho Kogyo Co Ltd
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Filing date
Publication date
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Application filed by Taiho Kogyo Co Ltd filed Critical Taiho Kogyo Co Ltd
Application granted granted Critical
Publication of USRE39377E1 publication Critical patent/USRE39377E1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • F16C9/00—Bearings for crankshafts or connecting-rods; Attachment of connecting-rods
    • 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
    • F16C33/1065—Grooves on a bearing surface for distributing or collecting 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
    • F16C2240/00—Specified values or numerical ranges of parameters; Relations between them
    • F16C2240/40—Linear dimensions, e.g. length, radius, thickness, gap

Definitions

  • the invention relates to a sliding bearing, and more particularly, to a sliding bearing in which annular peaks are formed on a surface which is disposed in sliding contact with a rotating shaft.
  • a slight clearance is provided between the surfaces of a sliding bearing and a rotating shaft which are disposed in sliding contact with each other when the rotating shaft is rotatably journalled by the sliding bearing.
  • a conventional sliding bearing when a smaller internal diameter of the surface of the sliding bearing which is disposed for sliding contact is chosen in an attempt to minimize the magnitude of the clearance, there results the disadvantage that a frictional resistance between the surfaces of the sliding bearing and the rotating shaft which are disposed in sliding contact with each other increases.
  • a larger inner diameter is chosen for the sliding surface of the sliding bearing to increase the clearance and minimize the frictional resistance, there is another disadvantage that the occurrence of an impact sound between the surfaces increases.
  • it has been difficult in a conventional sliding bearing to achieve a reduction in the frictional resistance between the sliding surfaces and a reduction in the impact sound simultaneously.
  • the invention provides a sliding bearing including a plurality of axially spaced, annular continuous or discontinuous peaks which extend circumferentially on a surface of the sliding bearing which is disposed for sliding contact with a rotating shaft in which, as viewed in an axial section, the various portions are defined on the basis of an imaginary reference line intersecting with individual peak regions and being parallel to the axis and is determined such that the total cross-sectional area of peak regions located above the reference line is equal to the total cross-sectional area of valley-shaped recess regions located below the reference line, the top of the peak having a height ⁇ C above the imaginary reference line and a height as measured from the bottom of the valley-shaped recess to the top of the peak being denoted by h , the parameter ⁇ C being taken on an ordinate and the parameter h being taken on the abscissa in a graphical representation, the parameters ⁇ C and h being located within a range defined by four rectilinear lines given by the following mathematical equation
  • a lubricant oil is stored in the space of an annular groove formed between a pair of axially adjacent peaks or in the valley-shaped recess, whereby the amount of lubricated oil which is maintained between the sliding surfaces can be increased. If the internal diameter of the sliding surface of the sliding bearing is small so as to reduce the clearance between the sliding surface of the rotating shaft and the sliding surface of the sliding bearing, the actual clearance between the rotating shaft and the sliding bearing is large as compared with the conventional sliding bearing, whereby the frictional resistance experienced between the sliding surfaces can be minimized.
  • the peaks on the sliding surface of the bearing and the clearance are effective in reducing the occurrence of an impact sound and, at the same time, the frictional resistance is reduced. In this manner, a reduction in the sliding resistance and a reduction in the occurrence of an impact sound are simultaneously achieved.
  • FIG. 1 is an axial cross section of an essential part of a sliding bearing 1 according to one embodiment of the invention is an exaggerated form;
  • FIG. 2 graphically shows a multitude of rectilinear lines, which illustrate differences in the size of essential parts between a sliding bearing according to the invention and a conventional sliding bearing;
  • FIG. 3 is the graphical representation of a result of measuring the impact sound in sliding bearings of several embodiments in contrast to that of a conventional sliding bearing;
  • FIG. 4 graphically illustrates the result of measuring the sliding resistance of a sliding bearing according to the embodiment of the invention in contrast to that of a conventional sliding bearing;
  • FIG. 5 graphically illustrates the results of measuring the oil quantity stored between the sliding surfaces in the sliding bearings of the invention in contrast to a conventional sliding bearing;
  • FIG. 6 is a chart indicating the results of measuring the back surface temperature of the bearing according to the invention as contrasted to a conventional sliding bearing;
  • FIG. 7 is an axial cross-section of part of a second embodiment of the invention.
  • FIG. 8 is an axial cross-section of part of a conventional sliding bearing.
  • FIG. 1 shows an axial section of a sliding bearing 1 according to the invention which assumes a cylindrical configuration, a sliding surface 1 A being shown.
  • the sliding surface 1 A is formed over its entire axial region where it is disposed in sliding contact with a sliding surface 2 A of a rotating shaft 2 , with a helical groove 1 B which is continuously circumferentially, thereby forming a peak 1 a between a pair of axially adjacent grooves 1 B.
  • peaks 1 a which are formed by the grooves 1 B, have a pitch p, which is chosen to be equal to 0.2 mm (200 ⁇ m).
  • a height h as measured from the bottom 1 b′ of each valley 1 b to the top 1 a′ of the peak 1 a, is chosen to be equal to 8 ⁇ m at the maximum.
  • the helical groove 1 B is formed by a boring operation, and the height of the top 1 a′ of each peak 1 a is determined in the following manner. Specifically, over the entire axial region of the sliding surface 1 A in which the helical groove 1 B is formed, an imaginary reference line L is determined which intersects the individual peaks 1 a and which extends parallel to the axis such that the total cross-section area of the individual peaks 1 a located above the reference line L is equal to the total cross-sectional area of the space comprising the individual valleys 1 b.
  • a height ⁇ C, as measured from the imaginary reference line L to the top 1 a′ of each peak 1 a, is chosen to be is a range from 1 to 8 ⁇ m.
  • a sliding bearing having a groove formed in its sliding surface is disclosed in Japanese Patent Publication No. 11,530/1988, for example.
  • the concepts of the height h , the reference line L and the height ⁇ C according to the present embodiment are applied to the sliding bearing disclosed in this Patent Publication, the relationship between the height h and ⁇ C are represented by rectilinear lines 10 and 11 .
  • a value corresponding to ⁇ C as termed in the present embodiment is equal to 15 ⁇ m.
  • FIG. 6 a groove which is trapezoidal in cross-section is shown in FIG. 6 thereof.
  • a value corresponding to ⁇ C will be 1.79 ⁇ m.
  • FIG. 2 a sliding bearing having a groove as indicated by phantom lines in FIG. 8 is located in a range below the rectilinear line 11 , which indicates the range of values for ⁇ C.
  • FIGS. 3 to 6 indicate results of experiments conducted by mounting the sliding bearing 1 of the present embodiment and the sliding bearing disclosed in the cited Patent Publication on a rotating shaft having an identical outer diameter with an equal clearance for rotation.
  • the clearance between the sliding surface 2 A of the rotating shaft 2 and the sliding bearing 1 refers to the dimension measured across the top 1 a′ of the peak 1 a and the sliding surface 2 A of the rotating shaft 2 .
  • experimental data shown in FIGS. 5 and 6 indicate that with the sliding bearing 1 of the present embodiment, the provision of the helical groove 1 B constructed in the manner mentioned above allows the quantity of lubricant oil, passing over the sliding surfaces 1 A and 1 B, to be increased.
  • the frictional resistance presented by the sliding surface 1 A can be reduced for the reason mentioned before, as indicated in FIG. 4 .
  • the occurrence of an impact sound between the sliding surface 1 A and 2 A of the sliding bearing of the rotating shaft 2 can be reduced, as indicated in FIG. 3 .
  • FIG. 7 shows a second embodiment of the invention.
  • the valley 1 b is in the form of a gentle arc in cross section.
  • the valley 1 b is trapezoidal in section.
  • the profile of the peak 1 a is in the form of a wedge having an acute angle in section.
  • the arrangement is similar to the first embodiment. Accordingly, similar experimental data are obtained as described in connection with the first embodiment, and therefore, a similar functioning and effect are achieved as in the first embodiment.
  • the peak 1 a is helically continuous as a result of the helical groove 1 B which continues in the circumferential direction of the sliding surface 1 A.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Oil, Petroleum & Natural Gas (AREA)
  • Sliding-Contact Bearings (AREA)
US10/210,813 1994-03-18 1995-03-17 Sliding bearing Expired - Lifetime USRE39377E1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
JP6073962A JP2795305B2 (ja) 1994-03-18 1994-03-18 すべり軸受
US08/553,584 US5704720A (en) 1994-03-18 1995-03-17 Sliding bearing
PCT/JP1995/000467 WO1995025904A1 (fr) 1994-03-18 1995-03-17 Palier a glissement

Publications (1)

Publication Number Publication Date
USRE39377E1 true USRE39377E1 (en) 2006-11-07

Family

ID=13533218

Family Applications (2)

Application Number Title Priority Date Filing Date
US08/553,584 Ceased US5704720A (en) 1994-03-18 1995-03-17 Sliding bearing
US10/210,813 Expired - Lifetime USRE39377E1 (en) 1994-03-18 1995-03-17 Sliding bearing

Family Applications Before (1)

Application Number Title Priority Date Filing Date
US08/553,584 Ceased US5704720A (en) 1994-03-18 1995-03-17 Sliding bearing

Country Status (5)

Country Link
US (2) US5704720A (de)
EP (2) EP1255053B1 (de)
JP (1) JP2795305B2 (de)
DE (2) DE69528805T2 (de)
WO (1) WO1995025904A1 (de)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20100054639A1 (en) * 2008-08-26 2010-03-04 Wolfgang Issler Slide bearing
US20130216162A1 (en) * 2010-11-02 2013-08-22 Yasuhiro Hikita Sliding bearing
US20130236134A1 (en) * 2010-11-17 2013-09-12 Doosan Infracore Co., Ltd. Sliding bearing having improved lubrication characteristics
US9261139B2 (en) 2013-02-06 2016-02-16 Trelleborg Sealing Solutions Us Friction-reducing geometric surface feature

Families Citing this family (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4204233B2 (ja) 2002-01-30 2009-01-07 日立粉末冶金株式会社 焼結含油滑り軸受および建設機械油圧ショベルまたはクレーン
JP3949117B2 (ja) * 2004-03-12 2007-07-25 大同メタル工業株式会社 すべり軸受
JP4271624B2 (ja) * 2004-06-23 2009-06-03 日立粉末冶金株式会社 建設機械の関節用すべり軸受
JP2006112479A (ja) * 2004-10-13 2006-04-27 Jtekt Corp 転がり摺動部品および転がり摺動部品の研磨方法
JP5020009B2 (ja) 2007-09-25 2012-09-05 大同メタル工業株式会社 すべり軸受
DE102007051774B4 (de) 2007-10-30 2018-08-02 Minebea Mitsumi Inc. Flüssigkeitslager mit verbesserten Abriebeigenschaften
DE102007058744B4 (de) 2007-12-05 2019-06-06 Federal-Mogul Wiesbaden Gmbh Gleitlagerschale sowie Lageranordnung
DE102008060369A1 (de) * 2008-12-03 2010-06-10 Bosch Mahle Turbo Systems Gmbh & Co. Kg Hydrodynamische Radialgleitlagerung
WO2012125714A1 (en) * 2011-03-15 2012-09-20 Flowserve Management Company Tapered channel macro/micro feature for mechanical face seals
WO2014104002A1 (ja) 2012-12-27 2014-07-03 大豊工業株式会社 摺動部材

Citations (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4400099A (en) 1981-02-06 1983-08-23 Miba Gleitlager Aktiengesellschaft Sliding surface bearing for heavy loads
US4538929A (en) 1982-09-20 1985-09-03 Miba Gleitlager Aktiengesellschaft Hydrodynamic sliding surface bearing
EP0155257A2 (de) 1984-02-27 1985-09-18 MIBA Gleitlager Aktiengesellschaft Verbundgleitlager
US4606653A (en) 1984-02-27 1986-08-19 Miba Gleitlager Aktiengesellschaft High-duty sliding surface bearing
JPS636215A (ja) 1986-06-23 1988-01-12 Nissan Motor Co Ltd 軸受
JPS6330619U (de) 1986-08-18 1988-02-29
JPS6353922U (de) 1986-09-29 1988-04-11
JPH02142921A (ja) 1988-11-21 1990-06-01 Komatsu Ltd 内燃機関用すべり軸受
US5071263A (en) 1989-10-13 1991-12-10 Taiho Kogyo Co., Ltd. Plane bearing
JPH0439461A (ja) 1990-06-06 1992-02-10 Toyota Motor Corp ガスタービン車の変速制御方法
JPH056412A (ja) 1991-06-28 1993-01-14 Nec Corp 対話配線方式
JPH058337A (ja) 1991-07-05 1993-01-19 Teijin Ltd 耐久性複合布
US5238311A (en) 1991-08-09 1993-08-24 Toyota Jidosha Kabushiki Kaisha Sliding bearing for an internal combustion engine
JPH0619850A (ja) 1992-06-30 1994-01-28 Casio Comput Co Ltd グラフ表示機能付き電子式計算機

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS59215996A (ja) * 1983-05-24 1984-12-05 Taiho Kogyo Co Ltd ロ−タリ−コンプレツサ−
JPH07108778B2 (ja) * 1986-06-30 1995-11-22 松下電器産業株式会社 光学ガラス素子の製造装置
JPS6330619A (ja) * 1986-07-22 1988-02-09 Mitsubishi Steel Mfg Co Ltd 板ばねの高次振動防止方法
US5141338A (en) * 1989-11-10 1992-08-25 Matsushita Electric Industrial Co., Ltd. Dynamic pressure type fluid bearing apparatus

Patent Citations (20)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4400099A (en) 1981-02-06 1983-08-23 Miba Gleitlager Aktiengesellschaft Sliding surface bearing for heavy loads
JPS6311530B2 (de) 1982-09-20 1988-03-15 Miba Gleitlager Ag
US4538929A (en) 1982-09-20 1985-09-03 Miba Gleitlager Aktiengesellschaft Hydrodynamic sliding surface bearing
AT385822B (de) 1984-02-27 1988-05-25 Miba Gleitlager Ag Verbundgleitlager
US4561787A (en) 1984-02-27 1985-12-31 Miba Gleitlager Aktiengesellschaft Composite sliding surface bearing
US4606653A (en) 1984-02-27 1986-08-19 Miba Gleitlager Aktiengesellschaft High-duty sliding surface bearing
JPS60205014A (ja) 1984-02-27 1985-10-16 ミバ・グライトラーガー・アクチエンゲゼルシヤフト 複合滑り軸受け
EP0155257A2 (de) 1984-02-27 1985-09-18 MIBA Gleitlager Aktiengesellschaft Verbundgleitlager
EP0155257B1 (de) 1984-02-27 1989-03-22 MIBA Gleitlager Aktiengesellschaft Verbundgleitlager
JPS636215A (ja) 1986-06-23 1988-01-12 Nissan Motor Co Ltd 軸受
JPS6330619U (de) 1986-08-18 1988-02-29
JPS6353922U (de) 1986-09-29 1988-04-11
JPH02142921A (ja) 1988-11-21 1990-06-01 Komatsu Ltd 内燃機関用すべり軸受
US5071263A (en) 1989-10-13 1991-12-10 Taiho Kogyo Co., Ltd. Plane bearing
US5116144A (en) 1989-10-13 1992-05-26 Taiho Kogyo Co., Ltd. Plane bearing
JPH0439461A (ja) 1990-06-06 1992-02-10 Toyota Motor Corp ガスタービン車の変速制御方法
JPH056412A (ja) 1991-06-28 1993-01-14 Nec Corp 対話配線方式
JPH058337A (ja) 1991-07-05 1993-01-19 Teijin Ltd 耐久性複合布
US5238311A (en) 1991-08-09 1993-08-24 Toyota Jidosha Kabushiki Kaisha Sliding bearing for an internal combustion engine
JPH0619850A (ja) 1992-06-30 1994-01-28 Casio Comput Co Ltd グラフ表示機能付き電子式計算機

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20100054639A1 (en) * 2008-08-26 2010-03-04 Wolfgang Issler Slide bearing
US8500334B2 (en) * 2008-08-26 2013-08-06 Mahle International Gmbh Slide bearing
US20130216162A1 (en) * 2010-11-02 2013-08-22 Yasuhiro Hikita Sliding bearing
US8858081B2 (en) * 2010-11-02 2014-10-14 Taiho Kogyo Co., Ltd. Sliding bearing
US20130236134A1 (en) * 2010-11-17 2013-09-12 Doosan Infracore Co., Ltd. Sliding bearing having improved lubrication characteristics
US8815407B2 (en) * 2010-11-17 2014-08-26 Doosan Infracore Co. Ltd. Sliding bearing having improved lubrication characteristics
US9261139B2 (en) 2013-02-06 2016-02-16 Trelleborg Sealing Solutions Us Friction-reducing geometric surface feature

Also Published As

Publication number Publication date
EP0709585B1 (de) 2002-11-13
DE69528805T2 (de) 2003-09-11
DE69535588T2 (de) 2008-05-15
EP1255053A3 (de) 2004-04-28
WO1995025904A1 (fr) 1995-09-28
EP1255053B1 (de) 2007-08-29
JP2795305B2 (ja) 1998-09-10
DE69535588D1 (de) 2007-10-11
JPH07259858A (ja) 1995-10-09
DE69528805D1 (de) 2002-12-19
EP0709585A4 (de) 1997-05-28
EP0709585A1 (de) 1996-05-01
US5704720A (en) 1998-01-06
EP1255053A2 (de) 2002-11-06

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