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Reciprocating system for simulating friction and wear
| Details |
Inventors: Akalin, Ozgen; Newaz, Golam M.;
Assignee: Wayne State University (Detroit, MI)
Primary Examiner: Choi; Kyle J.
Assistant Examiner:
Attorney, Agent or Firm: Rohm & Monsanto, P.L.C.
A bench testing system creates a predetermined wear and friction environment wherein wear elements, illustratively a piston ring and a cylinder liner, can be tested, along with lubricant properties, under simulated conditions of an internal combustion engine. The effects of speed and normal load can be examined under multiple lubrication regimes, and variations in the coefficient of friction can be observed as a function of crank angle degree. Profilocorder techniques are used to examine photomicroscopic surface characteristics. The cylinder wall wear element is supported in a first support arrangement that is driven reciprocatingly along a substantially axial path. A dynamic counter-reciprocating arrangement is coupled thereto for controlling second harmonic inertial forces. A second support arrangement that supports the piston ring wear element is coupled to a linear drive that urges same in a direction transverse to the substantially axial path of reciprocation of the cylinder wall wear element. A force gauge coupled to the linear drive produces data corresponding to the force being applied thereby. A further force gauge measures the friction force. Rotational data is obtained from a rotational encoder, and a lubricant supply arrangement provides lubrication in accordance with a plurality of lubrication regimes. |
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DETAILED DESCRIPTION FIG.
1 is a simplified schematic top plan view of a friction environment system 10 having a wear testing portion 11, a counter-balance portion 12, and a crank drive portion 13.
The crank drive portion is coupled via a shaft 15 and a pulley (not shown) to a motor 17 via a drive belt 19.
Wear testing portion 11 has a first support element 20 that is connected by a connecting rod 22 to crank drive portion 13.
As crank drive portion 13 is rotated by operation of motor 17, first support element 20 is driven by connecting rod 22 reciprocatingly in the direction of two-headed arrow 25.
The first support element is constrained to axial reciprocating motion by virtue of its coupling tool linear rails 27 and 28, which are maintained in fixed parallel relation to one another by rail supports 30.
A plurality of linear bearings 32 are coupled to first support element 20 and to respective ones of linear rails 27 and 28.
Thus, the first support element is constrained to linear motion, as noted hereinabove.
In this specific illustrative embodiment of the invention, counter-balance portion 12 is provided with a pair of counter-balance pistons 40 and 41 that are constrained by piston guideways 42 and 43 to travel in linear parallel paths of reciprocation in the direction of two-headed arrow 45.
Counter balance pistons 40 and 41 are coupled to crank drive portion 13 by respectively associated connecting rods 48 and 49.
As shown, the counter-balance pistons are arranged 180.
degree.
out of phase with the coupling of first support element 20 to the crank drive portion via connecting rod 22, and therefore the counter balance pistons travel in opposite directions of reciprocation with respect to the first support element.
This counter balancing action eliminates second harmonic inertial forces.
Crank drive portion 13 is itself balanced by balance weights 50 which serve to correct any residual unbalance therein.
In addition, crank drive portion 13 is shown to be coupled to a rotatory encoder 54 that produces an electrical signal responsive to the angular position of the crank drive portion
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