WO1988007620A1

WO1988007620A1 - Reciprocating piston engine

Info

Publication number: WO1988007620A1
Application number: PCT/DE1988/000196
Authority: WO
Inventors: Lothar Müller
Original assignee: Mueller Lothar
Priority date: 1987-03-30
Filing date: 1988-03-26
Publication date: 1988-10-06

Abstract

In a reciprocating piston engine, a torque is exerted through the cylinders, pistons and connecting rod on the lever arm formed by the bend in the crankshaft or a force is exerted on the pistons through the lever arm formed by the bend in the crankshaft and the connecting rod by rotation of the crankshaft. This engine is characterized in that the value of the said lever arm is increased or decreased by frictional engagement on each rotation of the crankshaft in order to improve the efficiency. The connecting rod bearing which engages in the crankshaft describes a structurally predetermined desired and therefore suitable path about the centre of rotation of the crankshaft. The point of application of the force on the crankshaft precedes the actual crank angle movement in the important phases of the working stroke. At top and bottom dead centre, the piston can be maintained completely or almost completely within structurally predetermined limits, despite further movement of the crank angle.

Description

Stroke piston machine

In spite of many improvements, reciprocating piston machines such as gasoline or diesel, two-stroke or four-stroke machines do not achieve a satisfactory level of utilization of the fuel energy used.

According to textbooks from technical universities, the share of energy in internal combustion engines is distributed as a percentage of the fuel energy supplied at full load as follows:

Diesel ship diesel

Highly charged petrol engine

Indicated work 33 - 35 40 - 43 45 - 48 exhaust energy 37 - 44 35 - 40 40 - 44

Wall losses 23 - 28 22 - 25 12 - 14

The values given here change very much during part-load operation.

After further deduction for personal use, friction, etc., only about 16% of the energy used by the fuel remains for the actual kinetic energy, i.e. the energy used for locomotion.

The invention has for its object to provide a reciprocating piston engine of whatever type that improves the energy portion of the supplied fuel energy in favor of the "indicated work" achieved and thereby reduce the proportions of the exhaust gas energy and the wall losses accordingly adorns or reduces the drive power required for the production of compressed air, for example.

This task is accomplished by a reciprocating piston machine in which a torque is generated by the cylinder (19), piston and connecting rod (5) on the lever arm formed by the crank (4) of the crankshaft or vice versa by the rotation of the crankshaft (6) via the by the crank (4) formed lever arm and the connecting rod (5) a force is exerted on the piston, according to the invention solved in that the point of application of the connecting rod (5) on the crank (4) non-positively into a desired more optimal orbit around the pivot point of the Crankshaft (6) is guided. The point of application does not describe a correctly circular path around the crankshaft axis, as has been customary so far, but is forcibly guided by guide rails (3) in guideways (1,16) in / or on the cranks (4) of the crankshaft (6), leading the crank angle guided. The point of application can be guided in any desired guideway around the pivot point of the crankshaft (6).

With this optional, non-positive and very low-friction guide and the point of contact of the connecting rod (5) on the crank (4) of the crankshaft (6) leading the actual crank angle movement by rolling in the guideways (1,16), e.g. can be achieved:

1. Hold the piston on the TDC with further crank angle movement.

2. Quasi, that is within the desired limits, holding the piston to the TDC with further crank angle movement. 3. Hold the piston on the UT with further crank angle movement.

4. Advance the point of engagement of the connecting rod (5) on the crankshaft (6) before the actual crank angle movement.

To 1 to 3

The crankshaft (6) is rotated further while the piston is being held or virtually being held at the TDC due to the pressure above the piston which rises within predeterminable limits.

The pressure curve over the piston can hereby be changed as compared to the known pressure curve for convenience.

This can achieve:

a. Optimization of the combustion process.

b. Optimization of the burn time.

c. Improvement of the gas exchange process.

d. Improvement of the charge ratio. (This will probably make the complex four-valve technology unnecessary)

e. Moving the max. Pressure over the piston to larger crank angles.

f. Improvement of exhaust gas values and reduction of fuel consumption. To 4

Due to the low friction loss advance of the connecting rod (5) in the guideways (1,16) of the crank (4) of the crankshaft (6), the actual crank angle movement is always effective during the decisive phases of the work cycle.

Table 1 at the end of the description shows this relationship for a design of a crank mechanism according to the invention, for example.

Here, e.g. beautiful :

At 2 ° crank angle (actually) a lever arm of 8 °

Crank angle.

At 5 ° crank angle (actually) a lever arm of 13 °

Crank angle.

At 10 ° crank angle (actually) a lever arm of 30 °

Crank angle.

Etc.

The invention thus achieves:

1. Improving the combustion process and the gas exchange ratios, increasing and, within limits, shifting the pressure curve over the piston.

2. Implementation of this increased pressure via a larger lever arm in relation to the stroke into a larger torque with the same crank angle movement or in total the same stroke. Guiding in the desired orbit of the connecting rod bearing, which engages non-positively on the crankshaft of the crankshaft, is achieved in that, for example, a shaft (9) is attached to the end of the connecting rod (5) engaging the crankshaft (6J), which is on both sides in guideways (1, 16) engages in the crankings (4) of the crankshaft (6) When the crankshaft (6) rotates, the desired path is determined by guide rails (3) into which the shaft (9) on the lower bearing of the connecting rod ( 5) engages on both sides via corresponding bearings (15).

The shape of the guide rails (3) in conjunction with the guide tracks (1, 16) formed in the crankings (4) of the crankshaft (6) achieves:

1. The piston remains at the dead centers;

2. advance the point of attack on the crankshaft;

3. Extension of the effective lever arm.

In the construction according to the invention, the crankshaft (6) is not, as usual, made of a continuous part. Since the shaft part, which connects the cranks (4) and on which the lower connecting rod bearing engages in the machines commonly used today, the crankshaft (6) is interrupted several times in multi-cylinder engines.

The interrupted crankshaft (6) in connection with a main drive shaft (2) (see below) is particularly robust, advantageous and much easier to manufacture than a continuous crankshaft (6).

In order for this crankshaft to be simple and, in the case of several cylinders, also repeatedly interrupted, the crankshaft in the ge given the usual task, a separate main drive shaft (2) is driven to jointly transmit power in several cylinders and to stabilize the multi-interrupted crankshaft (6) via gear pairs (10, 11) on the crankshaft (63). The speed of this main drive shaft (2) can be optimally predetermined for each desired application by selecting the gear ratio of these gear pairs (10, 11) between the crankshaft (6) and main drive shaft (2) with regard to the downstream transmission and differential.

The guideways (1,16) on or in the cranks {4) of the crankshaft (6) are shaped so that the pressure of the shaft (9) on the connecting rod (5) is always perpendicular to the guideways (1,16 ) acts, or counteracts the centrifugal force slightly above 90 °. This results in a precisely determinable curved or round shape for the guideways (1, 16) in or on the crankshaft cranks (4).

Only when the machine is at a standstill it is necessary to press the shaft (9) on the connecting rod (5) on both sides against the raceway of the ring-shaped guide rails (3) by means of a spring. During the run this is caused by the centrifugal force.

The shaft (9) on the connecting rod (5) is supported on both sides in the curved guideways (1, 16) of the crankshaft crankings (4), for example with two special plain or ball bearings (12, 13) with different diameters, see above that the guide always rolls closing at the top and bottom, or in the case of round guideways (16) with slide, roller or ball bearings (17). The roll on the Guide rails (33 for determining the desired raceway of the point of application of the connecting rod (5) in the crankings (4) of the crankshaft (6) are also made via two bearings (15) which are attached to the left and right of the connecting rod (53 on the shaft (9) The special bearings (15) rolling in the guideways (1, 16) and on the guide rails (3) are closed and designed in such a way that they bring little additional "pantsch losses" when immersed in oil. 15) was specified for this application as only 0.1-0.3% for the inner and outer rolling.

There is no complex adjustment mechanism and no complex redirection of forces. Only known and proven components are used for such machines, and thus a permanent load corresponding to today's machines is safe.

For a given cubic capacity, the reciprocating piston machine according to the invention achieves greater output or the required output with a smaller cubic capacity with a corresponding reduction in exhaust gas and wall losses via the larger total torque at the same speed.

The advance of the point of application of the connecting rod (5) to the crankshaft (6) has the effect that the pressure above the piston increased according to the invention by holding at TDC within desired limits in the important phases of the working cycle on a lever arm which is considerably larger than the conventional reciprocating piston machines .

In total, the projection in the direction of the force of the path covered on the periphery of the circular path is as large as or slightly larger than in the conventional design for a given stroke. By constructively determining the advance point of the connecting rod (5) on the crankshaft (6), a relatively larger or smaller distance traveled on the periphery of the circular path can be achieved in desired areas.

The same effect that the guideways (1) achieve in the cranks (4) of the crankshaft (6) can also be constructed with circular "round guideways" (163 in the cranks (4) of the crankshaft (6), which with the the connecting rod (5) attached shaft (9) are connected eccentrically.

There are two versions of the circular "round guideways" (16):

1. The shaft (9) located on the connecting rod (5) between the crankings (4) of the crankshaft (6) is firmly connected to the connecting rod (5).

No guide rails (3) are required to determine the orbit. The orbit is only determined by the eccentricity between the fixed shaft (9) on the connecting rod (5) and the round guideways (16) located at both ends of this shaft (see FIG. 5).

2. The shaft (9) engaging on the connecting rod (5) between the crankings (4) of the crankshaft (6) is rotatably connected to the connecting rod (5) via bearings.

The orbit of the point of engagement of the connecting rod (5) around the crankshaft axis is again indicated by the guide rails (3) described above. The balancing and lubrication of the machine according to the invention is ensured using known methods. The variable point of engagement of the connecting rod (5) on the crankshaft (6) must be balanced separately.

For the balancing of the crankshaft (6) the masses of the connecting rod plain bearing, the half connecting rod (5) and the strong shaft between the crankshaft crankings (4), which was previously caused by the design, are eliminated.

The rotating weight of the masses acting on the ring-shaped guide rails (3) by the centrifugal force can be e.g. are balanced completely by an equal, movable weight on the counterweights of the crankshaft crankings (4), guided by guide rails (3) which act in a reversed manner.

In the case of "boxer engines", the guide rails (3), which act in reverse, can be dispensed with.

The storage of the individual crankshaft pieces is possible two or three times depending on the embodiment.

In a further embodiment of the reciprocating piston machine according to the invention with a crankshaft (6) consisting of several, two or three-bearing shaft parts, the change in the lever arm of the crankshaft (6) is achieved in that a between the crank (4) of the crankshaft (6) additional crank (8) is attached.

This additional crank (8) is via a in the pivot point of the crankshaft (6), but independently of this supported on the motor housing, fixed gear and a rotatable on the crank (4) smaller gear GE leads that when rotating the crankshaft (6) drives a gear on the additional crank (8) so that the additional crank (8) is always horizontal when the cylinders are mounted on the crankshaft (6). This achieves the same goal as previously described, namely the extension of the lever arm during the work cycle. The bearing of the crankshaft piece in question is arranged within the gearwheel supported on the engine housing at the pivot point of the crankshaft (6) independently of the crankshaft (6).

In this embodiment too, an additional main drive shaft (2) is required due to the multiple interruption of the crankshaft (6). This embodiment can also be designed so that the lever arm in the middle of the compression stroke = 0 or even achieves a rotating effect beyond 0. In this embodiment, the connecting rod (5) again has the usual lower connecting rod bearing.

The invention is described below with reference to the drawings. Show it

Figure 1 shows a section of a first embodiment of the reciprocating piston machine according to the invention in a schematic representation; Figure 2 shows an example embodiment of the guide tracks (1) according to the invention; Figure 3 shows the bearing of the connecting rod (5) fixed shaft (9); Figure 4 shows a section along the line IV - IV of Figure 1; Figure 5 shows another embodiment of the guide track (16) according to the invention; Figure 6 shows another embodiment of the bearing on the connecting rod (5) located shaft (9); FIG. 7, for example, circular path guides around the pivot point of the crankshaft axis; FIG. 8 shows a further circular path guiding possibility around the pivot point of the crankshaft axis; FIG. 9 still another circular path guiding possibility around the pivot point of the crankshaft axis; Figure 10 is a calculated circular path around the pivot point of the crankshaft axis with a listing of the corresponding values over 180 ° crank angle movement; Figure 11 shows a constructive design of the guideway. (1) in the crank (4) of the crankshaft (6);

Figure 12 shows a further embodiment of the reciprocating piston machine according to the invention with additional cranking (8) of the crankshaft (6) in four different positions.

1 shows the connecting rod (5 (attached shaft (9) in its guideway (1) at the lower end of the indicated connecting rod). In addition, the example of a guide rail (3) is shown on which the connecting rod (5) engages the crankshaft The main drive shaft (2) is drivingly coupled to each crankshaft section (6) by means of a pair of gearwheels (10, 11), as can be seen in more detail in Figure 4. From Figure 1 it can be seen that the crankshaft ( 6) is laterally offset to the axis of the cylinder (12) In the illustrated position of the crankshaft (5) its effective lever arm is enlarged in relation to the stroke compared to conventional machines.

Figure 2 shows an example embodiment of the guide tracks (1) according to the invention on the crankshaft cranks (4) which, when the crankshaft (6) rotates, have different points of attack in these guide tracks (1) on a scale of 1: 1 and the leading point of the point of attack possible for this example Piston pressure through the connecting rod (5) on the crankshaft crank (4) of 20 ° crank angle.

Figure 3 shows the lower end of the connecting rod (5) with the laterally projecting stub shafts (9) for guidance via ball bearings (12, 13) in the guideways (1) of the cranked portions (4) of the crankshaft (6). Each stub shaft (9) carries outside two special ball bearings, of which the two outer ball bearings (12) have a smaller outer diameter than the two inner ball bearings (13). The two-sided guideways (1) in the cranks (4) each have a step (14) so that the ball bearings (12) and (13) can close and roll diametrically, ie the smaller ball bearing (12) outside the step (14 ) and the larger ball bearing (13) inside the step (14). The shaft stumps (9) also carry on the inside on both sides a further ball bearing (15) with which the shafts (9) roll on the guide rails (3), so that the desired annular path of the point of engagement of the connecting rod (5) in the crankings ( 4) the crankshaft (6) around the axis of the crankshaft (6) is determined.

According to Figure 4, the crankshaft (6), as far as shown, is interrupted twice. Each crankshaft piece is coupled to the main drive shaft (2) by means of a gear pair (10, 11). The guide rails (3), of which two pairs are shown in FIG. 4, are attached to the housing in a stationary manner (7). The connecting rods (5) are guided with their shaft ends on the inside via ball bearings in the guide rails (3). With their outer ball bearings, only one of which is indicated, they roll in the guideways (1) of the crankshaft crankings (4). Each crankshaft part (6) is supported twice.

FIG. 5 shows a further embodiment with the guide track (16) according to the invention on the crankshaft cranks (4), and the different points of application of the pressure above the piston when the crankshaft (6) rotates through the connecting rod (5) in these guide tracks (16). During the working stroke, the point of application of the connecting rod (5) hurries ahead of the actual angular movement of the crankshaft (6). The point of attack lags behind during the compression stroke. The one in the example. The resulting orbit (18) of the point of engagement of the connecting rod (5) on the crankshaft (6) shows a very flat behavior in TDC and LDC. This also gives the described advantages with regard to charge changes and the course of combustion.

FIG. 6 again shows the lower end of the connecting rod (5) with the laterally projecting shaft journals (9) firmly connected to the connecting rod, at the end of which there are round guide journals (1 6) which are offset eccentrically on both sides and which are located in the round guideways (16) of the crankshaft cranks (4) intervene stored. The storage can be done by means of impact-resistant slide, roller, ball or double ball bearings.

Figure 7 shows various ways of guiding the point of application of the connecting rod (5) around the crankshaft axis with different advance of the point of application, different holding times at TDC, different extension of the effective lever arm. Curve 1 describes the conventional circular path. Curve 2 shows, for example, a path of the connecting point of the connecting rod around the crankshaft axis. Curve 3 shows a further web guide, for example. Curve 4 shows, for example, the reduction in the effective lever arm length during the compression stroke. Furthermore, Figure 7 shows different offsets between the axis of the crankshaft (6) and the axis of the piston, "h ₁ " and "h ₂ " shows the possible difference of the distance traveled.

FIG. 8 shows a further possibility of guiding the connecting point of the connecting rod around the crankshaft axis, in which TDC is reached before 0 ° or 360 ° crank angle. FIG. 9 shows a further possibility of guiding the point of application of the connecting rod (5) around the crankshaft axis, in which the guideway only deviates from the conventional circular path in the range from 0 ° to 90 ° crank angle.

FIG. 10 shows a calculated, for example circular path guide in a circular path 103 for an example motor: stroke = 84 mm, bore = 90 mm ∅, connecting rod length = 120 mm, offset = 0 mm. Hold at TDC of up to 8 ° crank angle and maximum lead of the connecting rod on the crankshaft of 22 °. Due to the advance, e.g. with an actually traveled crank angle of 2 ° the lever arm of 8 ° crank angle. That means 5.92 mm lever arm instead of 1.47 mm. At a crank angle of 5 °, the lever arm acts at a crank angle of 19 °. That means 14.8 mm lever arm instead of 3.60 mm. At a crank angle of 10 °, the lever arm acts at a crank angle of 30 °. That means, instead of 7.47 mm, 25.33 mm lever arm. All values from 0 ° to 180 ° can be seen from the attached list.

FIG. 11 shows the design of the guideway (1) in the cranked crankshaft (6) for the example calculated according to FIG. 10 and the attached list. From this, the maximum advance of 22 ° and the extension of the radius r = 42 mm can be seen in this example during the advance of the point of application of the connecting rod up to r = 56.3 mm.

In the embodiment shown in FIG. 12 in four different crankshaft positions, an additional crank (8) is attached between the crankings (4) of the crankshaft (6) in such a way that it is always horizontal, as shown, when the cylinders (19) are mounted above the crankshaft as is the case with all four crankshafts shown Positions can be seen. During the working stroke (illustration C), the cranking (4) of the crankshaft (6) is extended by the additional cranking (8), while the cranking (4) and (8) subtract in position A and in positions B, and D the position of the crank (4) of the crankshaft (6) through the additional crank (8) in the

Height, i.e. the stroke, is not changed.

Computation runs cannot be carried out using the "p _mi formula" that is common today because it is smaller by 3 angular functions, but must be carried out using the somewhat more complex "Md formula", because this is the only way to recognize the effects of the lever arm, which is of different sizes in the important phases .

In reciprocating piston machines according to the invention, Md> p _mi !

Different variants of the reciprocating piston machine according to the invention are calculated and give e.g. A distribution of the energy shares in% of the fuel energy supplied as follows:

Diesel ship diesel

Highly charged petrol engine

Indicated work 50 - 67 60 - 72 70 - 77 Exhaust energy 30 - 21 25 - 17 23 - 17 Wall losses 20 - 12 15 - 11 7 - 6

If you e.g. Zt. Says that with an average of 34% of indexed work achieved by a reciprocating piston machine for personal use and other losses, another 18% lost go and only about 16% remain for the actual drive, you can also subtract 18% for your own needs and other losses in the calculated examples. This means: correspondingly smaller displacement to achieve the approx. 16% remaining today for the drive.

In addition to all current efforts to save fuel and reduce the environmental impact, the reciprocating piston machine according to the invention can bring about a further considerable reduction.

Calculation example:

Stroke piston machine stroke = 84 mm

Bore = 90 mm ∅ connecting rod length = 120 mm offset = 0 mm

In Table 1 below:

° KW = ° crank angle (actual)

Lead-in = the effective leading point of application of the connecting rod to the crankshaft in ° KW.

sin r = effective lever arm of a conventional reciprocating piston machine. r ₁ = radius according to the invention at the respective crank angle without leading and guideway = circular path 10 of FIG. 10.

r ₁ with lead = radius according to the invention at the respective crank angle with lead and guide track = circular path 10 of FIG. 10.

sin r ₁ = effective lever arm according to the invention of a reciprocating piston machine with lead, guideway = circular path 10 of FIG. 10.

r ₂ , = radius according to the invention at the respective crank angle without leading and guideway = circular path 2 of FIG. 7.

r ₂ with leading = radius according to the invention at the respective crank angle with leading and guideway = circular path 2 of FIG. 7.

sin r ₂ = effective lever arm with advance of a reciprocating piston machine according to the invention, guideway = circular path 2 of FIG. 7.

The crank drive variants on which this invention is based can be used anywhere in technology when a force which is currently acting has to be converted into a rotating force; eg bicycle pedals. _m

Claims

Patent claims - - - - - - - - - - - - - - - - - - - - - - - - - - - - - -

1. reciprocating piston machine, such as gasoline, diesel, two-stroke or four-stroke internal combustion engine or piston compressor, in which the cylinder arm (19), piston and connecting rod (5) exerts a rotating effect on the lever arm formed by the crank (4) of the crankshaft a force is exerted on the piston or by the rotation of the crankshaft (6) via the lever arm formed by its crank (4) and the connecting rod (5), characterized in that the point of application on the crankshaft (4) of the crankshaft ( 6) is positively guided into a desired orbit around the pivot point of the crankshaft (6).

2. reciprocating piston machine according to claim 1, characterized in that the point of engagement of the connecting rod (5) in the crank (4) of the crankshaft (6) is guided so that the piston remains at desired limits at TDC and TDC, or / and that TDC of the piston is reached before reaching 0 ° or 360 ° crank angle.

3. reciprocating piston machine according to claim 1 or 2, characterized in that the size of the effective lever arm increases or decreases with each revolution of the crankshaft (6) after appropriate effectiveness.

4. reciprocating piston machine according to claim 1 to 3, characterized in that the holding of the piston at TDC, with still increasing pressure above the piston by supporting on or in the rotating cranks (4) of the crankshaft (6), thereby in Acting direction of rotation is achieved.

5. reciprocating piston machine according to claim 1 to 4, characterized in that the point of engagement of the connecting rod (5) on guideways (1,16) in the crank (4) of the crankshaft (6) acting vertically, so that the effective point of attack in the range from 0 ° to over 90 ° crank angle leads the really traveled crank angle and thereby a lever arm that is correspondingly larger comes into effect than corresponds to the actual crank position.

6. reciprocating piston machine according to claim 1 to 5, characterized in that by advancing the point of application of the connecting rod (5) in the guideways (1, 16) of the crankshaft crankings (43), the effective projection of the distance traveled on the periphery of the circular path Way ahead of the really traveled crank angle in the desired and appropriate size.

7. reciprocating piston machine according to claim 1 to 6, characterized in that the connecting shafts between the crankings (4) of the crankshaft (6) are missing, on the crankings (4) Guideways (1,16) are formed and that at the end of the connecting rod (5) engaging the crankshaft (6) is a shaft (9).

8. reciprocating piston machine according to claim 1 to 7, characterized in that the on the connecting rod (5) attached shaft (9 (on both sides slide or ball bearing (15) which has two guide rails (3) the point of application of the connecting rod ( 5) on the crankshaft (6) into the desired shape of an orbit around the pivot point of the crankshaft (6).

9. reciprocating piston machine according to claim 1 to 8, characterized in that the connecting rod (5) attached shaft (9) between two crankings (4) of the crankshaft (6) on both sides of two ball bearings, needle bearings or other bearing types ( 12, 13) with different diameters engage in the guideways (1) and on each side in the guideways (1) a ball bearing (13) rolls up and the second ball bearing (12) closes below.

10. reciprocating piston machine according to claim 1 to 9, characterized in that the connecting rod shafts (9) in the guideways (1, 16) of the crankshaft crankings (4) with e.g. a spring is pressed outwards on both sides against the guide rails (3).

11. reciprocating piston machine according to claim 1 to 10, characterized in that the ball bearings, needle bearings or other bearing types (12,13) of the connecting rod shaft (9) at both ends, at one end or at no end of the guideways (1) close .

12. reciprocating piston machine according to claim 1 to 11, characterized in that the guide tracks (1,16) on the cranks (4) of the crankshaft (6) are shaped such that the pressure of the connecting rod (5) during the power transmission perpendicular to the guideways (1, 16) act or counteract slightly above 90 ° of the centrifugal force.

13. reciprocating piston machine according to claim 1 to 7 and 10, characterized in that the connecting rod (5) attached shaft (9) on both sides in the desired dimensions eccentrically to the shaft "round guideways" (16), the ball bearings, roller bearings or slide bearings (17) engage in the crankings (4) of the crankshaft (6).

14. reciprocating piston machine according to claim 1 to 7 and 13, characterized in that in the construction with "round guideways" (16) and thereby fixed shaft (9) on the connecting rod (5), the path that the point of application of the connecting rod to the Axis of the crankshaft describes, not by guide rails (3), but only by the eccentricity of the "round guideways" (16) to the fixed shaft (9) on the connecting rod (5).

15. reciprocating piston machine according to claim 1 to 8 and 13, characterized in that in the construction with "round guideways" (16) the desired path of the point of engagement of the connecting rod (5) about the axis of the crankshaft (6) by guide rails (3rd ) is determined and the connecting rod (5) rotatably engages the shaft (9) via a bearing.

16. reciprocating piston machine according to one of claims 1 to 15, characterized in that for the common power transmission in several cylinders (19) and for rotational stabilization of the multi-interrupted crankshaft (63 via gears (10, 11) a separate main drive shaft (2) is driven and the speed of the main drive shaft (2) by the choice of the ratio of the gears

(10,11) is optimally predetermined for each desired application.

17. reciprocating piston machine according to claim 1, 3 and 16, characterized in that the crankshaft (6) is interrupted several times, the crankshaft parts are each mounted two or three times and between the crankings (4) of the crankshaft (6) each an additional Crank (8) is attached.

18. reciprocating piston machine according to claim 17, characterized in that the additional crankings (8) are guided via gears so that the crankings (4) of the crankshaft (6) are extended by the additional crankings (8) during the working stroke, while of the compression stroke the crankings (4) of the crankshaft (6) are shortened by the additional crankings (8) and the additional crankings (83 do not extend the crankshaft crankings (4) at the top and bottom dead center of the piston.

19. reciprocating piston machine according to claim 17 or 18, characterized in that the additional crankings (8) are designed so that the effective lever arm during the compression stroke = 0 or even achieves a rotating effect beyond 0.