FI117906B - Plain bearing, in particular connecting rod for reciprocating internal combustion engines - Google Patents

Description

117906

Plain bearing, in particular connecting rod for reciprocating internal combustion engines.

The present invention relates to a plain bearing, in particular a connecting rod for reciprocating internal combustion engines having the features as defined in the main-5 concept of claim 1.

DE 198 01 200 C2 discloses a plain bearing for use in a connecting rod. The connecting rod described therein comprises the upper end of the connecting rod, the connecting rod arm and the connecting rod bearing, thereby forming a connecting member between the crank drive (pistons) and the connecting rod. The sliding bearing comprises a support frame consisting of a lower end of the connecting rod and a bearing holder of the connecting rod, in which a bearing strip formed as a complete bearing sleeve is placed in a transverse hole, and the sliding bearing is subjected to impact forces due to pressure fluctuations. This results in heavy bearing loads. Such external forces as well as thermal effects generally cause deformation of the bearing, in particular its bearing sleeve.

Oil for lubrication and cooling is fed in this type of sliding bearing, pressurized especially from the connecting rod inlet channels to the bearing sleeve, through the openings to the outside of the support frame, through the holes in the support frame, the connecting rod arm, and the lower end of the connecting rod.

As RPM and ignition pressure increases, such as occurs in new piston internal combustion engines, the clearance, i.e. the height of the so-called residual gap • between the bearing sleeve and the piston pin changes rapidly due to the crankshaft neck color • · * · 25. This means that •. * ··. oil pressure in this residual gap changes rapidly, which may cause cavitation effects on the inner shell surface of the bearing sleeve at its maximum impact and tensile load area and on the circumference of the connecting rod neck on this opposite side of the bearing sleeve. Therefore, it is very important to maintain the optimum shape of the 30 sliding bearings during operation.

: '** Experiments have shown that the connecting rod shape or model causes • · * different deformations. Many of the connecting rods have a concave, ie recessed and inwardly curved shape on the sliding surface of the bearing sleeve during use. • radial deformation, the other connecting rods exhibit a deformation of the bearing sleeve • · * · * 35, ie the convex or outwardly curved deformation of the bearing sleeve.

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It is therefore an object of the invention to provide a sliding bearing of this type which, in use, achieves an optimum bearing shape or, in use, forms an optimum bearing sliding bearing.

The problem is solved according to the invention so that the planar profile extending around the support surface 5 of the transverse bore of the support body, the flat bearing sleeve ridge and the smooth sleeve bearing surface of the bearing sleeve is concave / convex in the radial direction,

Thus, at least one bearing surface, either a transverse hole support surface of a support frame, a bearing sleeve brush or a bearing sleeve sliding surface, is formed according to the deformation expected during use of the plain bearing, which is due to the connecting rod used. optimally load-bearing plain bearing.

According to the deformation, at least one bearing surface is convex 15 or concave. This profile shape can be implemented on the sliding surface of the bearing sleeve, on the rear face of the bearing sleeve or both convex / concave or vice versa. The same effect is achieved when the transverse hole of the support frame: the support surface also has a similar concave / convex profile.

Another particularly advantageous effect of the plain bearing according to the invention is that the restrictions on the formation of the support body can be eliminated due to the corresponding profile of the bearing sleeve, which, regardless of the structure of the support body, reduces the thickness of the lubricating film.

* · 1 · •: 1: In the following, the slip bearing according to the invention will be described in greater detail by means of various embodiments with reference to the accompanying drawings. So, ···. Figure 1 shows a thread with a plain bearing according to the invention · 1 /; schematic cross-section of the tokange, · ·· I. / Fig. 2 shows a rotated view of the connecting rod * "** of Fig. 1, according to section S1 - S1, Fig. 3 shows a schematic view of the bearing strip of the bearing sleeve with the rotary: Fig. 4 shows a 90 ° rotated view of Fig. 3 according to section S3-S3 of the bearing strip and Fig. 5a-g illustrates, in a very simplified manner, other examples of a slide bearing according to the invention.

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Figs. 6a, 6b forms a sliding bearing support body 8. The support body has a transverse hole 9, the upper half of which extends above the lower part 5 of the lower end 5 of the connecting rod arm 5 and the lower half extends to the lower side of the lower arm 10.

The transverse bore 9 of the support body 8 has two bearing strips 12a, 12b forming a complete bearing sleeve 11 which surround the neck of the connecting rod not shown in the figure and leave a residual gap when sliding.

The pressurized oil 15 for lubrication and cooling is routed through the connecting rod neck to the bearing strips 12a, 12b, from where the oil passes through the oil holes 13 to the bearing sleeve 11, with at least one collector from the collecting chamber, the oil passes through the interconnected holes to the hole 14, which extends from the lower end 5 of the connecting rod 5 through the connecting rod 4 to the upper end 2 of the connecting rod.

Figure 3 shows in detail the bearing strip 12a of the bearing sleeve 11 having a lubricated sliding surface 15 by means of oil-hole 13 distributed in a circumference.

According to Fig. 4, said sliding surface 15 has a permeable or at least partially permeable U-shaped oil groove 16 for conducting the oil.

φ. · **. Said sliding surface 15 is concave so as to form a circular surface profile having a concave K in the radial direction of the sliding bearing.

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As described at the beginning, the shape of the connecting rod changes the deformation of the plain bearing, especially with respect to the bearing sleeve 11. In the exemplary connecting rod 1, external forces and thermal effects cause a convex deformation of the sliding surface 15 of the bearing sleeve 11, whereby the sliding surface 15 * * * is concave during operation.

Depending on the deformation of the plain bearing, a total * *. ···. Blood / convex profile on the support surface 18 of the transverse hole 9 of the support body 8, on the brush 17 of the bearing sleeve '* 35 or on the sliding surface 15 of the bearing sleeve 11.

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Depending on the deformation of the sliding bearing, a co-Vera / convex profile may be formed on the bearing surface 18 of the transverse bore 9 of the support body 8, on the sliding surface 15 of the bearing sleeve 17 or on the bearing sleeve 11.

Figures 5a-5h show different variations of the pro-5 profile formation of a concave / convex profile in the radial direction of the plain bearing.

Thus, according to Fig. 5c, the sliding surface 15 of the bearing sleeve 11 forms a convex surface profile which compensates for the concave deformation of the sliding surface 15 due to use.

The same effect can be achieved, as shown in Fig. 5b, by forming a convex surface profile extending around the bearing sleeve brush 17.

Fig. 5a shows an alternative embodiment of Fig. 4, in which a convex surface profile is formed in the bearing sleeve brush 17.

Finally, Figures 5d and 5e show a combination of a plurality of surface profiles in which a concave / ku-15 stern profile is formed on the sliding surface 15 and the bearing sleeve brush 17.

The counter body used in forming the sliding surface 15 in Figure 5c is already shown in Figure 4.

If necessary, even the support surface 18 of the support body 8 or its transverse hole 9 can be deformed, whereby a concave / convex surface profile is formed thereon according to the deformation of the sliding bearing 20.

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Claims (6)

1. Sliding bearing, in particular a crankshaft for piston combustion engines, comprising: a sliding bearing having a support body in which the diagonal hall bearing shell is provided which forms an entire bearing sleeve and which in part surrounds a shaft member to be supported, in particular a pin of the crank rod, with a residual gap in the form of a sliding surface at sliding contact, characterized by the sliding bearing having a surrounding concave / convex surface profile in relation to a support surface (18) of the diagonal tail (9) in the support body (8) and in relation to the even back (17) of a bearing sleeve; in relation to the sliding surface (15) of the bearing sleeve (11). Sliding bearing according to claim 1, characterized in that the sliding surface (15) of the bearing sleeve (11) has a circumferential concave surface profile, which compensates for a convex shape change of the sliding surface (15) conditional on use. Sliding bearing according to claim 1, characterized in that the sliding surface (15) of the bearing sleeve (11) has a circumferential convex surface profile, which compensates for a conditional change of shape of the sliding surface (15) which is in use. Sliding bearing according to claim 1 or 3, characterized in that the back (17) of the bearing sleeve has a circumferential concave surface profile. Sliding bearing according to claim 1 or 2, characterized in that: -. The back (17) of the gear sleeve has a circumferential convex surface profile. Sliding bearing according to claims 1-5, characterized in that the supporting surface (18) of the diagonal heel (9) in the supporting body (8) has a circumferential ··· concave / convex surface profile. ···· • 1 • · · · · · · · · · ··· * · · · · · ♦ 1 ··· · · · 1 · · · · · · · · · · · · · · · '• 1 ··· • · ♦ 1 • · · ··· * 1 • · • 1 · * 1 · · · 1 · ♦ · • ·… • · * ♦ · • · • · 1 · · ··· · · · 1 t • 1