DE4200412A1 - Piston engine working without crankshaft - has roller and disc drive to convert reciprocating motion to rotary movement. - Google Patents

Abstract

The movement of the piston (1) and the associated piston rod (5) is converted to rotary motion by an axially spaced curve drive or cam drive. Its face curves (4.1 and 4.2) are supported on a disc (7) secured in the engine housing. Oppositely tensioned roller pairs (2.1 and 2.2) run on the disc, the torque of which is delivered to a take-up or drive wheel (11) by roller bodies (8.1) moving in the guide channels (8.2) of the piston rod. USE/ADVANTAGE - Method of converting reciprocating into rotary motion suitable for single or multi-cylinder engines.

Description

The invention relates to the conversion of linear and going movement of a piston in an equal moderate shaft rotation or vice versa.

This movement transformation is in many areas mechanical engineering required such. B. piston compressor, Piston pumps, steam and gas piston engines, piston combustion motors, etc.

It is known to be necessary to accomplish this Movement conversion of the Kol moving in cylinder ben, crankshafts are mainly applied to the either using connecting rods or between them switch piston rods with cross heads and after Connecting rods realize this conversion. In doing so the connecting rods on the ver with the crankshaft journal tied ends laterally and perform a twist movement off, whereas the other ends with pistons connected, reciprocating, linear movements ren.

This results in the following disadvantages of using a crank piston machines equipped with shafts, due to the Movement and force relationships of the centric thrust crank gear:

• - variable tangential or rotational force from the deflection angle of the connecting rod and crank angle depends and near the O.T. (Top dead center) and the U.T. (bottom dead center) is zero.
• - variable normal force which either from the piston even in the cylinder or with an additional cross head and slideway is transmitted. This brings together liche friction work and reduction of mechanical Efficiency of the machine.
• - emergence of mass forces resulting from the acceleration movement and deceleration of the moving parts. Since the Elements of the crank mechanism different forms of movement execute (translation, rotation and coupling movements)  mass balance is particularly important but difficult to realize. This creates periodic dyna mix forces that give rise to vibrations and cause dangerous resonance phenomena, can machine foundations and stands, buildings influence negatively.

The invention has for its object a Kolbenbe path conversion from a linear reciprocating in a rotary movement and vice versa by means of an axial to create space cam gear the above Does not have disadvantages.

This task is carried out in generic facilities solved by the characterizing features of claim 1.

By axial forehead curves the symmetrical, in pairs brought, wavy elevations and the Realize two or four stroke processes in one revolution mutually tense roles move Couples using a torque roller sleeve linear movements of the piston in a rotary motion can convert.

The advantages that can be achieved with the invention consist mainly of:

• - Elimination of the piston side forces caused by the good guidance piston in the backlash-free axial space gear and centrically mounted torque rolling element bush, ver is caused. This allows the piston to be made smaller be and to reduce friction work and therefore to increase the efficiency of the machine wear.
• - Constant lever arm of the rotary transmission, which by the Geometric dimensions of the axial space gear set is.
• - Realizable complete mass balancing of the linear reciprocating and rotating moving parts. Therefore, the machine runs smoothly and the Vibration damping effort resulting in a reduction of the machine weight and foundation mass.

Some embodiments of the invention are in drawing shown and described in more detail below. It shows

Fig. 1 Scheme of the crankshaft-less power or working machine,

Fig. 2 forces and the direction of movement scheme,

Fig. 3 development diagram of the front curves - 2-pull method,

Fig. 4 development diagram of the front curves - 2-pull method with balance weight,

Fig. 5 development diagram of the front curves - 4-pull method,

Fig. 6 cylinder power or working machine,

Fig. 7 four-cylinder power or working machine,

Fig. 8 eight-cylinder star embodiment,

Fig. 9 multi-cylinder Boxer embodiment,

Fig. 10 multi-cylinder counter-piston version.

In Fig. 1, the invention which effects the conversion of the reciprocating piston movements into a rotary movement is shown schematically. The left half of the drawing is labeled "A", a piston engine with the piston ( 1 ) in the UT (lower dead center), whereas the right half of the drawing shows it in the OT (upper dead center). At the lower part of the piston ( 1 ) there is an extension in which an axis ( 3.1 ) is pressed in perpendicular to the piston axis. Pairs of rollers ( 2.1 ) with a tapered outer surface are mounted on the axially stub axles. These are based on a central forehead curve ( 4.1 ), which has a radial inclination angle (β). This is identical to the halved taper angle of the roller pairs ( 2.1 ) and the angle arms meet (at a common point on the piston axis so that a slip-free movement of the roller pairs ( 2.1 ) is made possible. The piston rod ( 5 ) is screwed into the center of the lower piston extension on which a cross arm with axially connected to it ( 3.2 ) is attached, which lie in one plane with the axles ( 3.1 ) and on which there are further pairs of rollers ( 2.2 ) which are located on a lower forehead curve ( 4.2 ) support, which is turned with the upper end curve ( 4.1 ), but rotated by half a division "T." These two end curves ( 4.1 ) and ( 4.2 ) are mounted on both sides on a support disc ( 7 ) which is clamped in the machine housing The lower roller pairs ( 2.2 ) can be pressed onto the lower end curve ( 4.2 ) by means of a screw connection ( 10.1 ) located on the piston rod ( 5 ), where occurs due to an internal tension between the upper pair of rollers ( 2.1 ) and the lower pair of rollers ( 2.2 ), which contributes to a play-free piston movement. Further down in the piston axis, the drive or driven wheel ( 11 ) is mounted, in which a torque rolling element bush ( 8 ) with pressing elements ( 8.1 ) is pressed.

The torque transmission between the linearly reciprocating piston ( 1 ) and piston rod ( 5 ), which are simultaneously brought into a rotary motion by the pairs of rollers ( 2.1 ) and ( 2.2 ) moving on the end curves ( 4.1 ) and ( 4.2 ) and the drive or driven wheel ( 11 ), is carried out by key ( 9 ) and torque rolling element bush ( 8 ) with rolling elements ( 8.1 ) which move in guide grooves ( 8.2 ) of the piston rod ( 5 ).

Fig. 2 explains only in a schematic manner the forces occurring between the pairs of rollers ( 2.1 ) and the end curve ( 4.1 ) and the direction of movement of the individual parts. The diagram shows that there is no normal piston force.

In FIGS. 3 to 5, the processing of the end curves (4.1) and (4.2) has been schematically shown with the piston guide and for a two-stroke cycle in Fig. 3 and 4 and for a four-cycle process in Fig. 5. Particularly erwäh nenswert is still the scheme in Fig. 4, which is a two-stroke method with mass balance for the elements in linear motion Be, represents. For this purpose, the additional roller pairs ( 2.3 ) and ( 2.4 ), which are rotated by 90 ° in relation to the roller pairs ( 2.1 ) and ( 2.2 ), are used. The constructive solution to this idea is shown in FIG. 6. The additional pairs of rollers ( 2.3 ) and ( 2.4 ) cause a counter-movement to the piston ( 1 ), piston rod ( 5 ) and the roller pairs ( 2.1 ) and ( 2.2 ) when rolling on the forehead curves ( 4.1 ) and ( 4.2 ). Fig. 6 shows a single cylinder engine or machine, "A" a cross section, "B" the piston ( 1 ) in the TDC (lower dead center) and "C" the piston ( 1 ) in the TDC (upper dead point) . It can be seen that the additional pair of rollers ( 2.3 ) and ( 2.4 ) and their axes ( 3.3 ) and ( 3.4 ) are perpendicular to the axes ( 3.1 ) and ( 3.2 ) and are fastened in nested forks ( 13.1 ) and ( 13.2 ) . These are mutually braced by screws ( 10.2 ). Since these forks ( 13.1 ) and ( 13.2 ) move in opposite directions to the piston rod ( 5 ), they are guided in slideways ( 14 ) in the piston ( 1 ). A counterweight ( 6 ) is attached to the forks ( 13.1 ) and ( 13.2 ) to balance the mass of the linear moving parts. The torque is transmitted from or to the input or output shaft ( 15 ) via the input or output gear ( 11 ) by means of backlash-free toothed belts.

FIGS. 7 to 10 include multi-cylinder power or Ar beitsmaschinen extending through complete mass balance of linear and rotating movement components characterization ren.

In Fig. 7, a four-cylinder Kraft or Arbeitsmaschi ne is shown in a circular arrangement, the drive or from drive wheels ( 11 ) of the cylinder units with a central drive or output gear ( 12 ), here as a spur gear Darge, which for play-free transmission of the torque is designed in two parts and mutually braced to work together. The pistons ( 1 ) of the opposite cylinder units must be linear in the same direction, whereas the laterally adjacent opposite movements must be carried out so that a complete mass balance is achieved.

Fig. 8 shows an eight-cylinder power or Arbeitsmaschi ne in a star arrangement. The drive or Ab drive wheels ( 11 ) of the individual cylinder units are designed as bevel gears, with a central drive or driven gear ( 12 ), the transmission for backlash-free torque can be moved axially, work together. Here, the pistons ( 1 ) of the opposing cylinder units must perform opposite, linear movements in order to achieve a complete mass balance.

In Fig. 9, an engine or work machine in boxer arrangement is shown. In this embodiment, the two torque rolling element bushes ( 8 ), against each other of the moving piston rods ( 5 ), are coupled together by a connecting bushing ( 16 ). The torque is then transmitted to the input or output shaft ( 15 ) via an input or output gear ( 11 ), in this case a bevel gear. If there are several cylinder units, they are connected to one another by backlash-free connecting wheels ( 17 ).

Fig. 10 shows a power or working machine in a counter-piston arrangement, in which the two torque rolling element bushes ( 8 ) are connected by play-free connecting wheels ( 17 ) to the input or output shaft ( 15 ).

Claims (3)

1. Piston movement conversion from a linear reciprocating into a rotary movement and vice versa by means of a space cam mechanism, characterized in that the movements of the piston ( 1 ) with its piston rod attached to it ( 5 ) positively into a rotary movement of a doubled movement, backlash-free axial space gears, whose end curves ( 4.1 ) and ( 4.2 ), which are mutually rotated by half a division "T" and can implement 2 or 4 stroke piston processes in one revolution, are supported on a support disc ( 7 ) fixed in the housing which move freely with screw connection ( 10.1 ), mutually braced roller pairs ( 2.1 ) and ( 2.2 ), and their torque is converted via a roller body bushing ( 8 ) by means of roller bodies ( 8. 1 ), which are in guide grooves ( 8.2 ) of the piston rod ( 5 ) because of and in a drive or driven wheel ( 11 ), is passed on. 2. Piston movement conversion according to claim 1, characterized in that in the case of single-cylinder machines, a pair of rollers ( 2.3 ) and ( 2.4 ) is additionally attached, the axes ( 3.3 ) and ( 3.4 ) of which are perpendicular to the axes ( 3.1 ) and ( 3.2 ) and in nested forks ( 13.1 ) u. ( 13.2 ) are attached, which are mutually braced by screw connections ( 10.2 ) and slide in the piston ( 1 ) in slide ways ( 14 ) and thereby move linearly in opposite directions to it, whereby by these forks ( 13.1 ) and ( 13.2 ) attached counterweight ( 6 ), the mass balance of linear moving parts can be achieved completely. 3. Piston movement conversion according to claim 1, characterized in that a complete mass balance of the linearly reciprocating masses can take place in multi-cylinder machines, if the star or circular arrangement of the cylinders, the drive or driven wheels ( 11 ) of the individual NEN cylinder units cooperate with a central drive or from drive wheel ( 12 ) and, in the case of a boxer arrangement, the torque rolling element bushes ( 8 ), the cylinder lying in a common piston axis through a connecting bushing ( 16 ) and, as in the case of machines in a counter-rotating piston arrangement with the drive or Output shaft ( 15 ) are coupled by connecting wheels ( 17 ).