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
  • F16C33/14—Special methods of manufacture; Running-in
• • 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
  • F16C17/022—Sliding-contact bearings for exclusively rotary movement for radial load only with a pair of essentially semicircular bearing sleeves
• • 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
  • F16C33/1045—Details of supply of the liquid to 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
  • F16C2220/00—Shaping
  • F16C2220/60—Shaping by removing material, e.g. machining
• • 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
  • F16C2220/00—Shaping
  • F16C2220/60—Shaping by removing material, e.g. machining
  • F16C2220/62—Shaping by removing material, e.g. machining by turning, boring, drilling
• • 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
  • F16C2220/00—Shaping
  • F16C2220/60—Shaping by removing material, e.g. machining
  • F16C2220/66—Shaping by removing material, e.g. machining by milling
• • 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
  • F16C2220/00—Shaping
  • F16C2220/80—Shaping by separating parts, e.g. by severing, cracking
  • F16C2220/82—Shaping by separating parts, e.g. by severing, cracking by cutting

Definitions

• the invention relates to a bearing shell with a carrier material made of metal, in particular steel, which is coated with at least one plain bearing material.
• the invention also relates to the use of such bearing shells, to a bearing which is composed of such bearing shells and to a manufacturing method of bearing shells.
• Such bearing shells are used in particular in internal combustion engines, in crankshaft bearings and connecting rod bearings.
• these bearing shells can have oil holes and in the sliding surface, i.e. have oil grooves in the plain bearing material. These oil grooves are connected to the oil holes and are milled into the bearing material.
• Such oil grooves usually extend over the entire inner circumference of the bearing shells.
• oil grooves are arranged in the back of the bearing, these are large-sized bearing shells for marine diesel engines, the oil grooves each extending over the entire circumference of the bearing shell.
• Newer car engine concepts provide for a changed oil flow, in which the lubricating oil has to be led around the bearing shell.
• Experiments with oil grooves in the bearings have turned out to be complex and costly.
• Another disadvantage is that such grooves have to extend from the bearing housing to the bearing cover, so that a weakening of material in the area between the bearing housing and bearing cover leads to stability problems.
• the available space is very small due to the retaining screw located there.
• From DE 33 28 509 C1 plain bearing elements are known which have fine channels as drainage channels for liquid lubricant on the back of the bearing, which occupy a maximum of 15% of the contact area. The depth is specified as 0.03 to 0.2 mm.
• This measure is intended to prevent the build-up of oil carbon between the back surface of the bearing and the receiving bore without the machine parts receiving the bearing and the elements holding the bearing bore together. ⁇ strengthened, and thus must be trained more heavily.
• the lubricant penetrating between the seat surfaces can move towards the free ends of the seat surfaces in the course of the relative movement. Accordingly, all drainage channels must open on the axial end edges of the slide bearing element. These drainage channels are therefore not suitable for targeted oil routing. No statement is made about the type of production of the drainage channels. .
• This object is achieved with a bearing shell in which at least one oil-bearing groove is embossed in the back of the carrier material.
• the groove preferably extends from a bearing shell end over a section of the outer circumference of the bearing shell. It is not necessary for these new engine concepts that the groove extends over the entire outer circumference of the bearing shell, because the oil supply and discharge channels in the bearing housing or the bearing cover are generally arranged in the region of the apex of the bearing shells.
• the groove extends circumferentially, i.e. parallel to the axial end faces of the bearing shell.
• the groove preferably opens into the partial surface of the bearing shell.
• the groove preferably extends over a circumferential angle range of ⁇ 1 120 °, in particular over a circumferential angle range of ⁇ ⁇ 90 °, this angular range being calculated from the partial area.
• the depth T max is preferably ⁇ 0.8 D, where D denotes the thickness of the carrier material.
• the depth and the width of the groove depend on the requirements regarding the quantity of the oil to be guided, whereby on the other hand care must be taken that only slight deformations of the bearing material occur when the groove is impressed. This is described in more detail in connection with the method.
• the plain bearing material preferably consists of an aluminum alloy, a sintered bronze or a cast bronze.
• Preferred materials are AlSn ⁇ , CuAI7, Cu80Sn10Pb10 or Cu80Sn10Zn10.
• At least one intermediate layer can also be provided between the carrier and the slide bearing material.
• An overlay layer on the plain bearing material is also possible.
• the bearing which is constructed from two bearing shells according to the invention, provides that the two bearing shells are arranged relative to one another in such a way that the partial surfaces into which the grooves open lie on one another.
• the bearing shells are preferably used in the main bearing of an internal combustion engine or an internal combustion engine.
• the material strips are cut off along dividing lines perpendicular to the tape feed direction, the material strips extending perpendicular to the feed direction or parallel to it, depending on the bandwidth. In the latter case, the bandwidth corresponds to the width of the strip of material that has been cut off.
• the material strips can be processed before or after forming.
• the grooves are embossed with their longitudinal axis preferably perpendicular to the tape feed direction, which is in line with one of the conventional workflows in the production of bearing shells, as strips of material extending perpendicularly to the tape feed direction are separated one after the other and are subsequently formed into bearing shells. If the material strips extend in the feed direction, the grooves are accordingly also stamped with their longitudinal axis in the feed direction.
• Grooves with a continuously decreasing groove depth are preferably embossed.
• the plain bearing material is preferably applied to the carrier material with an increased oversize.
• the thickness of the bearing material is brought to its final dimensions.
• embossing of grooves in the strip material leads to an expansion and curvature of the strip in the strip plane due to the material displacement. Since the conventional processing machines are designed for processing straight strips, it is advantageous if at least one compensating embossing is introduced on the side of the strip opposite the groove.
• This compensation embossing is carried out in such a way that a comparable material displacement occurs in the band plane, as occurs when the groove is embossed.
• care must be taken to ensure that the stamping of compensating grooves does not lead to increased material waste if the area of the compensating grooves has to be separated from the material.
• a wedge-shaped groove is preferably embossed as a compensation embossing, the tip of which points to the opposite side of the band, where the groove is embossed.
• the belt curvature can also be accepted if the subsequent tool for the material strip separation is adapted accordingly. In this case, there is no need to stamp compensating grooves.
• FIG. 1 shows a perspective view of a bearing shell
• Figure 2 shows a section along the line A-A. by the bearing shell shown in Figure 1.
• Figure 3 shows a bearing consisting ..i-, a ⁇ s; zw, ei bearing shells in perspective,
• FIGS. 4a and 4b top views ⁇ a, on, material strip. , the tape processing according to a first embodiment.
• a bearing shell 1 can be seen in perspective, which has a metallic carrier material 2, here steel, which is coated with a sliding bearing material 3, which forms the sliding surface 5.
• the two upper end faces of the bearing shell 1 are referred to as partial surfaces 4a, 4b.
• a groove 6 extends over a section 8 of the outer circumference of the bearing shell 1.
• the groove 6 is stamped into the carrier material 2 and, as can be seen in the region of the partial surface 4a, has a trapezoidal cross-section (see also FIGS . 2 and 3).
• Partial area 4a has the groove 6 its maximum depth, which decreases along the groove, so that the groove 6 runs out at its end 6 'and merges into the surface of the carrier material 2.
• the groove 6 runs parallel to the axial end faces of the bearing shell.
• FIG. 2 shows a section along the line AA of the bearing shell 1 shown in FIG. 1.
• the groove 6 extends over a circumferential angle region 8 of the outer circumference of the bearing shell 1.
• the maximum depth T max of the groove 6 is reached in the region of the partial surface 4a, where the groove 6 opens into the partial surface 4a.
• the depth T decreases continuously over the circumferential angle range 8, which is approximately 80 ° in the embodiment shown here.
• the maximum depth T max is approximately 0.4.D, where D denotes the thickness of the carrier material.
• the bearing shell shown in FIG. 2 additionally has an oil hole 7a in the apex of the bearing shell.
• FIG. 3 shows a bearing 9 consisting of two bearing shells 1 in a perspective view.
• the two bearing shells 1 are arranged in such a way that the two grooves 6 of the upper and lower bearing shells 1 merge into one another and thus form a common groove.
• FIG. 4a shows a material strip 10 in plan view, which consists of a carrier material 2 coated with slide bearing material 3 and which is moved in the feed direction 11. This is a straight material strip 10, the two edges 16, 17 of which are aligned parallel to one another.
• Such a material strip 10 which has the composite of carrier material 2 and slide bearing material 3, is fed to an embossing station 12, as is schematically indicated in FIG. 4b.
• embossing station 12 a groove 6 extending perpendicular to the feed direction 11 is embossed, a compensation embossing 14 in the form of a wedge-shaped groove being introduced in the region of the dividing line 13.
• the dividing line 13 denotes the line on which the material strip 15 is cut off in a later operation.
• the separated material strip 15 'forms an intermediate product from which the finished bearing shell 1 is formed.
• the compensation embossing 14 is wedge-shaped, so that the greatest material displacement occurs at the edge 16 of the band 10. If one were to dispense with these compensating embossings 14, the band 10 would warp and, after the embossing of a plurality of grooves 6, would assume the curved shape shown in broken lines, which is identified by the reference symbol 10 '.
• the parallelism of the edges 16 and 17 of the band 10a can be maintained despite the impression of the grooves 6. It is important to ensure that the maximum width of the wedge-shaped grooves 14 corresponds approximately to the width of the grooves 6.

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)
• Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)

Applications Claiming Priority (3)

Publications (1)

Family

ID=32114945

Family Applications (1)

Country Status (5)

Families Citing this family (13)

Family Cites Families (21)

• 2002
  • 2002-10-30 DE DE10250474A patent/DE10250474B4/de not_active Expired - Fee Related
• 2003
  • 2003-10-23 EP EP03775083A patent/EP1606524A1/de not_active Withdrawn
  • 2003-10-23 JP JP2004547418A patent/JP2006508302A/ja not_active Withdrawn
  • 2003-10-23 WO PCT/DE2003/003544 patent/WO2004040155A1/de active Application Filing
  • 2003-10-23 US US10/533,102 patent/US20060002643A1/en not_active Abandoned

Non-Patent Citations (1)

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