Bearings – Rotary bearing – Plain bearing
Reexamination Certificate
1999-10-29
2001-07-10
Hannon, Thomas R. (Department: 3682)
Bearings
Rotary bearing
Plain bearing
C384S288000
Reexamination Certificate
active
06257768
ABSTRACT:
The present invention relates to half-shell bearings for internal combustion engines.
Half-shell sliding bearings generally employ a so-called “nick” or “notch” to provide axial location of the bearing shells in their housings, usually either the connecting rod (conrod) housings and/or the main bearing housings, in the engine. The nick is a small portion of the bearing wall adjacent the joint face and either at one end face or intermediate the bearing end faces which is sheared and moved in a radially outwardly direction relative to the bearing circumference and which locates in a machined recess in the bearing housing. As mentioned above, the purpose of the nick is to provide accurate axial location of the bearing in its housing and, in some cases, to provide a fool-proof assembly method, for example to prevent a cap half-shell being fitted to the block and vice versa where the two half shells differ. The nick is not intended to prevent rotation of the bearing within the housing, rotation being prevented in most cases by the degree of interference between the bearing back and the housing.
However, it is becoming increasingly common for production engines to employ “nickless” bearings.
The absence of a nick presents problems in the case of racing engines. Racing engines operating at high rotational speeds suffer from distortion of the housings due to the high loads generated and in this instance the nick not only provides axial location but also does provide some measure of resistance to circumferential movement of the bearing shells relative to their housing. Racing engine designers are not therefore, prepared to use nickless bearings in racing engines. In some racing applications bearings employing two nicks are used.
Where rotation of the bearing has been experienced, fracture of the nick portion can occur and there is a case for nicks having an increased projected area to resist rotational force to be used, however, for manufacturing reasons this is rarely possible.
There are however disadvantages in having a nick in the bearing and these disadvantages are accentuated in the case of racing engines.
Firstly, the recess in the bearing bore due to the nick can cause breakdown of the hydrodynamic oil film which, in any case, is usually considerably thinner than on normal production engines.
Secondly, the presence of the nick disrupts the the bearing joint face and therefore causes a localised region of poor clamping between the bearing halves with a consequential reduction in contact pressure on the bearing back in this area.
Thirdly, the recess required in the bearing housing to accommodate the nick can act as a stress raiser and cracking in this region between the recess and the bolt hole is not unknown. Again, this particular problem is exacerbated in racing engines due to the greater stresses involved.
Thus, it is an object of the present invention to provide a bearing or a bearing and housing assembly wherein the bearing has greater resistance to rotation relative to its housing whilst not incurring the above mentioned disadvantages of nicks.
According to a first aspect of the present invention, there is provided a combination of a bearing and a housing for said bearing in an internal combustion engine, the bearing including two substantially semi-circular half-bearing shells comprising a first half-shell bearing having a first wall thickness and a second half-shell bearing having a second wall thickness wherein said first wall thickness is different from said second wall thickness and said first and second half shells have a substantially common bore diameter when assembled in said housing.
The “wall thickness” of a bearing is its total thickness including any constituent layers such as steel backing layer and alloy bearing layer for example. The bearing may comprise more than two layers.
The housing of the bearing and housing combination of the present invention may comprise a portion machined into a cylinder block or crankcase part of the engine or alternatively in a conrod (hereinafter referred to as “block”) to accept one of the first or second half-shells and a corresponding “cap” part to accept the other half-shell. Since the wall thicknesses of the first and second half-shells are different from each other and the bore diameter is substantially the same it follows that the outer diameters of the first and second half-shells are different and that the block and cap housing parts have corresponding bore diameters to receive the shells.
The axes of the centres of curvature of the bores of the block and cap parts must be coincident.
In the combination of the present invention, part of the joint face of the thicker half-shell butts up against the joint face of the housing of the other half-shell thus preventing rotation of the bearing pair. The bearing half-shells of the present invention do not require nicks and consequently the bearings do not suffer from the disadvantages set out above.
Half bearings in their free state when not clamped together in a housing are slightly longer in circumferential length than their corresponding housing part. This is known as “crush” and is to allow the joint faces of two bearing halves to contact each other and exert a force to push them securely into their respective housings and create an interference fit therebetween. In the thicker of the two half-shells of the present invention, the joint face over the additional diameter compared with the other half shell may be relieved to enable good contact between the bearing half-shell joint faces to permit satisfactory clamping.
According to a second aspect of the present invention, there is provided a bearing comprising a pair of half-bearing shells including a first half-bearing shell and a second half-bearing shell each having a common bore diameter when in use but having different wall thicknesses from each other.
REFERENCES:
patent: 2821444 (1958-01-01), Brown
patent: 4025131 (1977-05-01), Bergquist et al.
patent: 5072707 (1991-12-01), Takai et al.
patent: 5788380 (1998-08-01), Niegel et al.
patent: 27 23 585 (1977-05-01), None
patent: 36 19 404 (1986-06-01), None
patent: 195 10 928 (1995-03-01), None
patent: 2 754 023 (1996-09-01), None
patent: 1577562 (1980-10-01), None
patent: 2209566 (1989-05-01), None
patent: 2324838 (1998-11-01), None
Dana Corporation
Hannon Thomas R.
Rader & Fishman & Grauer, PLLC
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