Compensating device for the reciprocating first-order mass forces of a crank mechanism

Description

Compensation device for the reciprocating inertial forces of the first order of a crank mechanism The invention relates to a Compensation device for the reciprocating inertial forces of the first order in a crank mechanism. It is known that the masses of the first order moving piston machines by oppositely reciprocating masses or balanced by two counter-rotating masses of the same size. The masses revolving in the opposite direction of rotation require. own bearings and drives and are therefore impractical. Movable auxiliary masses are used to compensate for reciprocating auxiliary masses Eccentric discs, which are mounted eccentrically on the crankshaft, and balancing weights have been proposed, by eccentric discs or cranks in. Straight guides, which are designed as slideways, are moved back and forth. These are costly and prone to failure construction elements required. The invention has a device for the complete mass balancing of the reciprocating inertial forces of the first Order of a crank mechanism, preferably created for single-cylinder piston engines, in which on the crankshaft, preferably on both sides of the Cranks, secondary cranks, eccentric disks or the like are attached, move the balancing weights back and forth in time with the crank revolutions, the inertia force changing in the crank cycle is balanced by the combined inertial force effect of one of the secondary cranks or Eccentric discs, e.g. B. via connecting rods, perpendicular to the direction of movement of the reciprocating mass of the crank mechanism with go' Phase shift moving additional mass and a z. B. arranged on the extended Xurbel cheeks, with the crank revolving, balancing mass. According to the invention with phase shift moving balancing mass articulated, preferably guided by trailing arms, approximately in a straight line. The reciprocating moving masses behave inversely like the eccentricities causing their movement and their static moments inversely like their distances from each other. Sliding guides are avoided by the articulated linear guide. The unfavorable lubricating conditions in the occurring, relatively small movements have rendered the prior art arrangements practically unusable. The drawing shows in Fig. i a schematic sketch to explain the general idea of ​​the invention and in the Fig. 22, 3 and 4 practical examples in and side elevation for a one- and a two-cylinder internal combustion engine. According to Fig. i, a crank mechanism 2 moves the piston via the connecting rod 4 5 in the cylinder 6. Right and left of the crank 2' with the radius R are secondary cranks 7 and 7*' with the. Radii r 'arranged in the direction of R, the via connecting rods. 9 and g' a shaft io articulated on both sides in guides i i and i r' perpendicular to the direction of movement of the piston 5 move.. The crank webs are, as usual, extended backwards and carry counterweights on these extensions at a distance r" from the crank Wave:2nd The forces of the reciprocating masses of the single-cylinder crank mechanism, which are to be balanced, come from the piston as well Piston pin or cross head and the proportion of the connecting rod. These crowds like. have the size H. On the wave io is the Balancing mass H 'arranged perpendicular to the direction of movement of the mass H and by appropriate arrangement of the secondary cranks 7 and 7 'with go' phase shift in relation to the movement of the mass H is moved. The inertia forces therefore complement each other to a beat of Crank:2' circulating inertia force, which is caused by the counterweights circulating at the rear ends of the crank web from the total mass H' am effective radius r" can be compensated. The radii or eccentricities r 'of the side cranks and i` the circulating mass H' must meet the condition: r' - R' = r" - H' = R - H. For according to the invention, the mass H' is approximately straight-lined by means of handlebars or the like. It is sufficient because the very small movements of twice the frequency can be neglected, especially since they do not affect the mass balance of the first-order forces remain influential. From Abh.: 2 and 3 an embodiment of the invention for a single-cylinder engine can be seen. The reference numbers for the Crank mechanism parts are the same as in fig. i. The balancing mass H' is guided by linkage springs i i and i i`. The construction according to the invention can. can also be carried out several times, whereby first-order moments of inertia balance each other out, let the z. B. occur in two- and three-cylinder engines. Fig. 4 shows the arrangement according to the invention, as for a normal two-cylinder in-line engine in order to balance the forces of the force couple by means of a device according to Fig. i. Fig. 3 represents in this 1 is a section through the cylinder 6b. 1 is the distance between the masses H reciprocatingly moved in the cylinders 6" and 6b, and 1' is the distance between the centers of gravity of the balancing weights H' provided for each cylinder, then the following condition applies for the correct dimensioning of H': r' - H' - l' = R - H - 1.

Claims

[0008] PATENT CLAIMS-. i . Compensating device for the reciprocating first-order mass forces of a crank drive, preferably for piston engines, in which auxiliary cranks, eccentric discs or the like are mounted on the crankshaft, preferably on both sides of the crank. are attached to move the balancing masses back and forth in time with the crank revolutions, whereby the mass force changes with the crank stroke This is balanced by the combined mass force effect of one of the auxiliary cranks, or eccentric discs4 e.g. via connecting rods, perpendicular to the direction of movement of the reciprocating mass of the crank mechanism with phase shift, additional mass and a counterweight, e.g. arranged on the extended crank webs and rotating with the crank, characterized in that the The counterweight (H), which moves with phase shift, is guided in an approximately straight line, preferably by linkage springs (ii, i i').

2. Device according to claim i, characterized in that the reciprocating masses (H, H') move in the opposite direction to their movement causing eccentricities (R, r').

3. Device according to claims 1 and 2, applied to double or triple crank drives, characterized by the fact that the static moments (H - R or H' - r) of the reciprocating masses (H, I#') are inversely proportional to their Distances (1, 1') from each other. Considered publications: German Patent Specifications Nos. 117 809, 695 757, 824 722, 887 444, 835 110.