WO2005038277A1 - Palier lisse pour un arbre - Google Patents

Palier lisse pour un arbre Download PDF

Info

Publication number
WO2005038277A1
WO2005038277A1 PCT/DE2004/001693 DE2004001693W WO2005038277A1 WO 2005038277 A1 WO2005038277 A1 WO 2005038277A1 DE 2004001693 W DE2004001693 W DE 2004001693W WO 2005038277 A1 WO2005038277 A1 WO 2005038277A1
Authority
WO
WIPO (PCT)
Prior art keywords
lubricant
bearing
shaft
capillary
bearing body
Prior art date
Application number
PCT/DE2004/001693
Other languages
German (de)
English (en)
Inventor
Martin Huber
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 WO2005038277A1 publication Critical patent/WO2005038277A1/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
    • 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
    • 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
    • F16N—LUBRICATING
    • F16N7/00—Arrangements for supplying oil or unspecified lubricant from a stationary reservoir or the equivalent in or on the machine or member to be lubricated
    • F16N7/12—Arrangements for supplying oil or unspecified lubricant from a stationary reservoir or the equivalent in or on the machine or member to be lubricated with feed by capillary action, e.g. by wicks
    • 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
    • F16N—LUBRICATING
    • F16N2210/00—Applications
    • F16N2210/14—Bearings

Definitions

  • the invention relates to a plain bearing for a shaft with at least one bearing.
  • Sintered plain bearings are used in particular for DC motors and for high-speed AC motors, i.e. those made of sintered iron or sintered bronze, the material structure of which, due to the manufacturing process, has a large number of pores and cavities into which a lubricant, such as oil, is incorporated in the course of an impregnation process. is brought, which serves to lubricate the bearing.
  • a lubricant such as oil
  • a disadvantage of these oil-impregnated sintered bearings is that there is no defined lubricant delivery, but rather the lubricant delivery depends on the surface condition of the bearing point and the shaft, the thoroughness of the lubricant dipping process during manufacture, the concentricity of the shaft within the plain bearing, the temperature of the bearing point and the viscosity of the Lubricant depends. Furthermore, the release of lubricant from the sintered material onto the sliding point depends on the speed of the shaft. Another disadvantage is that the amount of lubricant that is made available to the bearing point depends on the absorption capacity of the sintered material. Another disadvantage is that the lubricating properties are inadequate when the shaft starts to cold, because of the viscosity the one in the sintered material!
  • the lubricant introduced does not guarantee uniform wetting of the bearing point and the shaft at very low temperatures. It is also disadvantageous that the lubricant introduced into the sintered material tends to paste over time, as a result of which an adequate amount of lubricant is no longer provided at the bearing point.
  • the plain bearing according to the invention offers the advantage that at least one lubricant depot designed as a cavity is provided inside the bearing body, which allows the absorption of a larger amount of lubricant, it being provided that due to its size, this lubricant depot does not act capillary with regard to the lubricant introduced , As a result, a sufficiently large amount of lubricant can be made available over a long period of time and under different operating conditions.
  • the slide bearing consists of at least two bearing body parts which touch one another in a sectional plane running through the slide bearing, the surfaces of the bearing body parts facing one another being designed as contact surfaces.
  • the contact surfaces of the at least two bearing body parts are flat surfaces that face each other and that are perpendicular to the longitudinal axis of the shafts.
  • the bearing can therefore be easily assembled from the two bearing body parts.
  • At least one capillary and / or the lubricant depot is formed in the area of the contact surfaces.
  • an easy manufacture of the capillary and / or the lubricant depot is achieved, since the contact surfaces are easily accessible as surfaces of the bearing body part before the assembly of the at least two bearing body parts, and therefore the formation of these elements can be carried out in a simple manner, for example by simple surface machining - such as drilling, grinding, milling or by spark erosion. It is also possible to design these elements in the manufacture of the bearing body parts.
  • the lubricant depot is formed by at least one first depression in at least one of the contact surfaces.
  • the lubricant depot is formed by simple surface processing, namely the application of at least one recess by any suitable processing method.
  • the capillary is formed by at least one further, second depression in at least one of the contact surfaces.
  • the depression or the depressions become self-contained volumes.
  • the lubricant depot and the capillary are connected to one another, so that the capillary opens into the lubricant depot.
  • the capillary is formed between the lubricant depot and the shaft or bearing point, so that between the lubricant depot and the shaft or the bearing point there is a connection which acts capillary with respect to the lubricant and which supplies the lubricant for Deposit allowed.
  • the capillary is arranged radially to the shaft axis.
  • a lubricant depot is assigned to each capillary in the case of a plurality of capillaries. This ensures that even if a lubricant depot or a capillary fails, the bearing point is supplied with lubricant from other capillaries and / or other lubricant depots of the same bearing.
  • the capillary leads to the shaft or to a lubricant cavity assigned to the shaft.
  • lubricant is supplied to the bearing point over a larger area, so that sufficient wetting of a sufficiently large bearing point area with lubricant is ensured, in particular when the cold starts up or at high speeds.
  • a lubricant depot is assigned to several capillaries.
  • a rather large-volume lubricant depot therefore interacts with a large number of capillaries, preferably independently of position and in terms of volume.
  • the lubricant depot is designed as a depression which surrounds the shaft in an annular manner in at least one of the bearing body parts. This forms, for example, a circumferential channel or a half torus, the equatorial plane of which is formed by the contact surface. It is precisely in this way that a particularly position-independent supply of lubricant is achieved if the capillaries are arranged radially to the shaft axis and are evenly spaced around them, since a lubricant supply takes place in every position which the plain bearing can assume in space and in particular around the shaft axis.
  • One embodiment of the invention provides that in addition to the presence of the lubricant reservoir and the capillaries, the bearing body part material itself is impregnated with lubricant.
  • a preferred embodiment of the invention provides that the bearing body parts have rotary aligning means for their relative position to one another, so that not only easier, precise fitting can take place, but also ensures that, for example, half-formed recess contours form a whole in each bearing body part put together in alignment.
  • fitting lugs and / or fitting types can be provided on the circumference of the bearing body parts, which result in an unmistakable, form-fitting fit. As a result, the bearing body parts can be clearly aligned with one another.
  • the slide bearing material as a whole is soaked with the lubricant.
  • the lubricant depot can also be easily filled by vacuum-soaking the entire plain bearing with the lubricant in a conventional manner. Not only are the pores of the material filled with the lubricant, but also larger cavities within the bearing body, in particular namely the lubricant depot and the capillary. Advantageous embodiments are mentioned in the subclaims.
  • Figure 1 is a slide bearing consisting of two bearing body parts in longitudinal section through the axis of a shaft;
  • Figure 2 shows a contact surface of a bearing body part in supervision
  • Figure 3 shows another contact surface of another bearing body part in supervision
  • Figure 4 shows another contact surface of another bearing body part in supervision.
  • FIG. 1 shows a plain bearing 1 for a shaft 2, with a bearing body 3 which consists of two bearing body parts, namely the upper bearing body part 4 and the lower bearing body part 5.
  • the bearing body parts 4 and 5 each have a surface 6 which is opposite to the other bearing body part and which - lying one on top of the other - in the state shown in FIG. 1 forms a contact surface 7 in a sectional plane 8 of the plain bearing 1.
  • the bearing body parts 4, 5 face each other in such a way that they touch areas of the surface and outside edge-tight with the contact surfaces 7.
  • Each bearing body part 4, 5 has at least one bearing point 9.
  • the bearing point 9 is in direct contact with the shaft surface 10 of the shaft 2.
  • the shaft axis 11 of the shaft 2 is also shown.
  • the following description relates to a left or right side of a bearing body part 4, 5 in FIG. 1 with respect to the shaft axis 11.
  • Each surface 6 of a bearing body part 4, 5 forming a contact surface 7 has a first depression 12 and a second depression 13.
  • the second depression 13 is connected to the first depression 12.
  • the first depression 12 and the second depression 13 are ring contours around the shaft axis 11.
  • the bearing body parts 4, 5 are opposite to the cutting plane 8 with the contact surfaces 7 in mirror image.
  • the first depression 12 of the lower bearing body part 5 and the first depression 12 of the upper bearing body part 4 are also mirror images of the sectional plane 8. The same applies to the second recess 13 of the bearing body parts 4, 5.
  • the first depression 12 of the upper bearing body part 4 forms a cavity 24 with the first depression 12 of the lower bearing body part 5, namely the lubricant reservoir 14.
  • Both the lubricant reservoir 14 and the capillary 15 are accordingly designed as ring contours around the shaft axis 11.
  • the lubricant depot 14 thus has a toroidal or approximately toroidal cross section.
  • the capillary 15 is designed as a very flat ring contour, so the distance from its inner to its outer diameter is considerably greater than its clear height. With its end facing the shaft 2, the capillary 15 opens into a lubricant cavity 16 formed along the shaft 2 up to the bearing point 9, the mouth 17 resulting.
  • annular tapping 19 is formed, which surrounds the shaft 2 and forms a lubricant volume 20.
  • the bearing point 9 surrounds the shaft 2 in a ring shape, so that it touches the shaft surface 10 with only slight play.
  • the bearing body parts 4, 5 also have rotary alignment means 21, which are formed opposite one another either as a fitting nose 22 or as a receptacle 23.
  • the fitting lug 22 and the receptacle 23 can still be moved freely with respect to one another.
  • the area shown on the left in FIG. 1 shows this state of the rotary alignment means 21 before final assembly.
  • the receptacle 23 is positively connected to the fitting nose 22, which can be done, for example, by a shaping or pressing process.
  • the manner in which the rotary alignment means 21 is designed and whether or in what way a final fixation takes place is not important for the function of the invention.
  • Any suitable rotary alignment tool can be considered. It is also conceivable to provide either a releasable or no fixed connection of the bearing body parts 4, 5 via the rotary alignment means 21. In the latter case, the plain bearing 1 can then be easily dismantled again, for example for revision purposes.
  • the required concentricity of the bearing body parts 4, 5 with respect to one another can also be produced after the positive connection by means of a calibration process or another suitable method.
  • the slide bearing 1 is completely filled with a lubricant, not shown, for example with an oil, by vacuum soaking.
  • all cavities are filled, apart from the pores of the material, in particular also the lubricant reservoir 14, the capillary 15, the lubricant cavity 16 and the lubricant volume 20.
  • the lubricant is fed from the lubricant depot 14 to the bearing point 9 due to the capillary action of the capillary 15 without further action, in particular without external intervention.
  • Lubricant is available via the lubricant cavity 16 over a large area of the shaft surface 10 facing the capillaries 15, so that large-area prewetting already takes place and the lubricant film between the bearing point 9 and the shaft surface 10 is prevented from tearing off.
  • Lubricant expelled from the bearing point 9 during the operation of the shaft 2 in the direction of the end region 18 of the slide bearing 1 collects in the ring tapping 19 designed as a lubricant volume 20 in the end region 18 of the bearing body part 4, 5 prevents the lubricant from being finally lost through expulsion from the slide bearing 1 along the shaft surface 10 beyond the end region 18 of the slide bearing 1. Sufficient lubrication is also ensured between the end region 18 of the sliding bearing 1 and the shaft surface 10.
  • lubricant depot 14 With changing pressure and temperature conditions inside and outside the plain bearing 1, lubricant becomes once preferably driven from the inside to the outside, ie from the lubricant cavity 16 via the bearing point 9 to the lubricant volume 20, but once inside, ie from the lubricant volume 20 to the lubricant cavity 16 and also back into the lubricant depot 14.
  • FIG. 2 shows a plan view of a lower bearing body part 5 at the level of a contact surface 7 or cutting plane 8.
  • a shaft 2 shown here in cross section is assigned a plurality, namely two lubricant depots 14, each with its own capillary 15 and its own lubricant cavity 16.
  • Both the lubricant depot 14 and the capillary 15 and the lubricant cavity 16 can advantageously by means of a suitable machining process, for example by machining a surface 6 of the bearing body part 5 such as drilling, milling, spark eroding or a combination thereof, or already during the forming process of the bearing body part 5 are formed as a first depression 12 and a second depression 13.
  • the respective cavity 24 of the lubricant depots 14 and the capillaries 15 is created when the bearing is assembled by placing an upper bearing body part 4 of mirror-image design, which has corresponding first depressions 12 and second depressions 13.
  • the lubricant depot 14 and the capillary 15 are only formed as half a volume, but the plain bearing 1 is once again simplified and cheaper to produce.
  • the lubricant is supplied to the shaft surface 10 and the bearing point 9 via the capillary 15 and the lubricant cavity 16.
  • FIG. 3 shows a plan view of a lower bearing body part 5 with a shaft 2, at the level of a contact surface 7 or cutting plane 8.
  • the lubricant reservoir 14 is designed as a first depression 12 of the surface 6, the first depression 12 being arranged essentially concentrically around the shaft axis 11 in the bearing body part 5, that is to say forming an annular contour with an at least approximately half-toroidal cross section.
  • the capillaries 15 are each arranged as second recesses 13 radially towards the shaft axis 11 towards the lubricant reservoir 14.
  • the capillaries 15 are evenly spaced from one another, so they each enclose the same angle ⁇ . Small deviations in the size of the angle ⁇ are insignificant for the function of the exemplary embodiment.
  • This embodiment provides a particularly position-independent and reliable supply of the bearing 9 and the shaft surface 10 with the lubricant, not shown in detail, since the lubricant, not shown in detail, is constant regardless of the position that the plain bearing 1 or the shaft 2 can assume in space reaches the bearing point 9 from the rather large-volume lubricant depot 14 via at least one but usually several capillaries.
  • a reduced inflow from a capillary 15 is easily compensated for by an increased inflow from another capillary 15, since there is a self-contained pressure system between the lubricant reservoir 14, all the capillaries 15 emanating therefrom and the bearing point 9.
  • the respective cavity 24 of the lubricant depots 14 and the capillaries 15 is created, as before during assembly of the bearing, by placing an upper bearing body part 4 which is embodied as a mirror image and has corresponding first depressions 12 and second depressions 13.
  • an upper bearing body part 4 which is embodied as a mirror image and has corresponding first depressions 12 and second depressions 13.
  • the lubricant depot 14 and the capillary 15 are only formed as half a volume, but the plain bearing 1 is once again simplified and cheaper to produce.
  • FIG. 4 shows a lower bearing body part 5 with a shaft 2 as well as lubricant depots 14 and capillaries 15, which are produced as above, and which are not arranged symmetrically and non-uniformly on the surface 6 of the bearing body part 5 or around the shaft 2.
  • lubricant depots 14 and capillaries 15 which are produced as above, and which are not arranged symmetrically and non-uniformly on the surface 6 of the bearing body part 5 or around the shaft 2.
  • an embodiment which is particularly suitable for reliable lubricant supply can be formed by capillaries 15 and lubricant deposits 14 which differ in number and shape.

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  • 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)

Abstract

L'invention concerne un palier lisse (1) pourvu d'au moins un point d'appui (9) pour un arbre (2). Selon la présente invention, ce point d'appui (9) est relié, par l'intermédiaire d'au moins un capillaire (15), à au moins un dépôt à lubrifiant (14) sous forme de cavité (24), situé dans le corps (3) du palier et sans effet capillaire en raison de sa dimension.
PCT/DE2004/001693 2003-09-25 2004-07-28 Palier lisse pour un arbre WO2005038277A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE2003144589 DE10344589A1 (de) 2003-09-25 2003-09-25 Gleitlager für eine Welle
DE10344589.7 2003-09-25

Publications (1)

Publication Number Publication Date
WO2005038277A1 true WO2005038277A1 (fr) 2005-04-28

Family

ID=34428127

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/DE2004/001693 WO2005038277A1 (fr) 2003-09-25 2004-07-28 Palier lisse pour un arbre

Country Status (2)

Country Link
DE (1) DE10344589A1 (fr)
WO (1) WO2005038277A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102007023107A1 (de) 2007-05-16 2008-11-20 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Kurbelwellenlagerung einer mehrzylindrischen Brennkraftmaschine
EP2441972A3 (fr) * 2010-10-12 2013-05-08 Newcera Technology Co., Ltd. Palier pour rotation à grande vitesse
EP2436939B1 (fr) * 2010-09-30 2016-08-31 Newcera Technology Co., Ltd. Module de lubrification hybride

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102007019978B3 (de) 2007-04-27 2008-10-23 Kronotec Ag Bauplatte, insbesondere Fußbodenpaneel, und Verfahren zu deren Herstellung
CN102465964B (zh) * 2010-11-16 2015-07-08 汶莱商新瓷科技股份有限公司 混合式润滑组件
CN102465963B (zh) * 2010-11-19 2015-06-24 汶莱商新瓷科技股份有限公司 高负载轴承
CN102465965B (zh) * 2010-11-19 2015-07-08 汶莱商新瓷科技股份有限公司 高转速轴承
TWI461613B (zh) * 2012-01-10 2014-11-21 Newcera Technology Co Ltd 微型潤滑組件
DE102014011632A1 (de) 2014-08-01 2016-02-04 Daimler Ag Lagerungsanordnung eines Hauptpleuels für eine Hubkolbenmaschine sowie eine Hubkolbenmaschine
DE102017208752A1 (de) 2017-05-23 2018-11-29 Zf Friedrichshafen Ag Schmiermittelfördereinrichtung mittels Kapillarwirkung

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE596413C (de) * 1932-04-28 1934-05-04 Bbc Brown Boveri & Cie Schmiervorrichtung fuer Gleitlager mit am Umfang der Lagerschale verteilten Schmierloechern zur Schmierung mit fluessigem Schmiermittel
DE663245C (de) * 1935-01-08 1938-08-03 Siemens Schuckertwerke Akt Ges Lager mit aus Scheiben gebildetem Lagerkoerper
GB571103A (en) * 1943-12-04 1945-08-07 Bound Brook Bearings G B Ltd Improvements relating to anti-friction bearings
GB898877A (en) * 1959-09-07 1962-06-14 Ford Motor Co Improved bearing
US3264045A (en) * 1964-01-02 1966-08-02 Gen Electric Lubrication system for dynamoelectric machines
GB1084404A (en) * 1966-03-18 1967-09-20 Federal Mogul Corp Chambered self-lubricating bearing
US20020146183A1 (en) * 2001-04-10 2002-10-10 Chien-Jung Chen Bearing device

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DE916738C (de) * 1938-06-22 1954-08-16 Dr Hans Vogt Selbstschmierendes Kapillarlager
DE952942C (de) * 1948-10-02 1956-11-22 Duesseldorfer Eisenhuettengese Aus Sintermetall bestehendes selbstschmierendes Lager und Verfahren zu seiner Herstellung
US2700209A (en) * 1950-02-15 1955-01-25 Michigan Powdered Metal Produc Process of making self-aligning powdered metal bearings
US3110085A (en) * 1957-12-11 1963-11-12 Gen Electric Method of making self-lubricating bearings
FR1471780A (fr) * 1966-03-18 1967-03-03 Federal Mogul Corp Palier auto-lubrifiant
DE19937567A1 (de) * 1998-09-11 2000-03-16 Bosch Gmbh Robert Sintergleitlager für Motoren und Getriebe

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE596413C (de) * 1932-04-28 1934-05-04 Bbc Brown Boveri & Cie Schmiervorrichtung fuer Gleitlager mit am Umfang der Lagerschale verteilten Schmierloechern zur Schmierung mit fluessigem Schmiermittel
DE663245C (de) * 1935-01-08 1938-08-03 Siemens Schuckertwerke Akt Ges Lager mit aus Scheiben gebildetem Lagerkoerper
GB571103A (en) * 1943-12-04 1945-08-07 Bound Brook Bearings G B Ltd Improvements relating to anti-friction bearings
GB898877A (en) * 1959-09-07 1962-06-14 Ford Motor Co Improved bearing
US3264045A (en) * 1964-01-02 1966-08-02 Gen Electric Lubrication system for dynamoelectric machines
GB1084404A (en) * 1966-03-18 1967-09-20 Federal Mogul Corp Chambered self-lubricating bearing
US20020146183A1 (en) * 2001-04-10 2002-10-10 Chien-Jung Chen Bearing device

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102007023107A1 (de) 2007-05-16 2008-11-20 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Kurbelwellenlagerung einer mehrzylindrischen Brennkraftmaschine
EP2436939B1 (fr) * 2010-09-30 2016-08-31 Newcera Technology Co., Ltd. Module de lubrification hybride
EP2441972A3 (fr) * 2010-10-12 2013-05-08 Newcera Technology Co., Ltd. Palier pour rotation à grande vitesse

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