DE3226396A1 - Rotary engine - Google Patents

Abstract

The invention relates to a rotary engine with the characteristics that, in a rotationally symmetrical housing (12, 13, 14) with cylindrical inner chamber with a first shaft (15) of constant circumferential speed lying in the axis of the rotation housing, a first section of a disc of constant circumferential speed, designed as a piston (16) and extending in a radial direction rotates and opposite on a likewise axial second shaft (17) a second section of a disc, likewise designed as a piston (18) and extending in a radial direction, rotates at a different speed of rotation to the first piston (16) in such a way that the piston (18) in the engine working on the four-stroke principle stops for the induction, rotates at a greater circumferential speed than the first piston (16) for the compression, then also stops for the working stroke and again rotates at a greater circumferential speed than the first piston (16) for the exhaust. <IMAGE>

Description

PATENT ADVOCATE DR; -! ^ G-; ' Έ D U a "RD

01.07.1982 5 COLOGNE 1, Dr.B./str

Werderstrasse 3 Telephone (0221) 524208-9

Br 206

Registration number. please specify

Patent application

the gentlemen

Matthias Strang

5358 Bad-MUns i.ereifel-Kirspenich, Fabrikstrasse Wilhelm Josef Biermanri

5350 Euskirchen, Hubertusstrasse 34

"Rotary piston engine"

The invention relates to a rotary piston engine.

Rotary piston engines are known in many embodiments. The most famous rotary piston engine according to Felix Wankel is a four-stroke internal combustion engine in which a triangular Piston in an oval housing, slightly constricted in the middle, like a planet on a circular path, rotating at the same time, revolves so that the piston with the wall of the housing three chambers are constantly changing Volume forms. The three sides of the piston of equal length

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are curved outwards. During the revolution, the triangular points of the piston are constantly in contact with the center wall. The center of the equilateral triangular piston describes a closed circle during its rotation. The center of this circular path coincides with the center of the Epitroschoids together. The piston thus performs a rotary movement around an axis, the axis moving on a circular path. The circular path of the piston is indicated by a causes the shaft mounted centrally in the motor housing, which in the Area of the piston is designed as an eccentric. The rotary movement of the piston around a circular path generated by the eccentric is enforced by an equal! This is on one side inside the piston an internal toothing arranged on a fixed, connected to the motor housing The pinion rolls off. The ring gear and thus the piston are arranged eccentrically with respect to the pinion. During one revolution of the eccentric, the ring gear moves around the pinion accordingly. The Wankel engine described above takes place at every full revolution (360 °) of the eccentric shaft an ignition.

This results in a non-uniformity of the torque curve, which has to be compensated for by appropriate centrifugal masses. By stringing together several motor cells arise a multiple motor, so that high performance can be achieved with little construction effort with small motor dimensions. In the case of this multiple motor, the result is the offset by 180 ° Eccentric a balanced torque curve as

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in the previously described engine with only one piston. The structure and mode of operation of the rotary engine described above shows that it is compared to conventional piston engines with crankshaft and connecting rods from comparatively few There are components, but these asymmetrical components are very difficult to manufacture and at high cost are. The Wankel engine also has the disadvantage that the rotary piston is protected from its sealing strips at the edges is worn, which are therefore subject to a correspondingly high level of wear.

The present invention is based on the task of creating a rotary piston engine which consists of only a few components, the bodies of revolution are so that they are easy to manufacture. At the same time, the pistons should be used without significant additional effort exist twice, so that a balanced torque curve is guaranteed. Furthermore, it should also be possible to line up several motor cells on a common shaft.

To solve this problem, a rotary piston engine proposed according to the invention that in a rotationally symmetrical Housing with a cylindrical interior with a first, lying in the axis of the rotating housing shaft with a constant Peripheral speed designed as a first piston, rotating disk extending in the radial direction and on the opposite side of a second shaft, which is also coaxial

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a second, also designed as a piston, is in Radi al direction extending disc rotates with the first piston against different rotational speeds in such a way that it stands still for the intake of the four-stroke engine, for compression greater circumferential speed than the first piston rotates, also stands still on the working stroke and for pushing out again at a higher peripheral speed than the first Piston rotates.

The rotary piston engine according to the invention consists of rotationally symmetrical Elements, such as the cylindrical cylinder room with curves whose circumferential surfaces are bodies of revolution and Shafts that are not eccentric, so that in terms of movement or rotation, the pistons around in the same way Spatially located waves rotate. This enables the production of the components forming the rotary piston engine simple.

In a further embodiment according to the invention, it is proposed that that the suction over an angle of approx. 60 °, the compression over an angle of approx. 120, the working stroke over a Angle of approx. 60 and the pushing out over an angle of approx. 120 °. However, these values can be changed.

These stipulations result in sufficient times for suction, compression, the working stroke and also for pushing out. It is particularly important that to push out the

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burned gases an angle of 120 ° is available, so that careful pushing out is guaranteed. There at the same time the pistons are bodies of revolution and are arranged around coaxial shafts between the working surfaces of the piston column of varying widths, but which expand in the direction from the inside to the outside, is a careful pushing out of the burned gases guaranteed.

The solution according to the invention enables the suction openings with a width extending coaxially in the axial direction, but also in a sufficient circumferential direction can be, so that despite a high circumferential speed sufficient suction can take place. In the same way, those arranged in the stationary housing can also be used Outlets extend over a sufficiently dimensioned width extending in the axial direction and also in the circumferential direction of the housing extend sufficient length so that sufficient pushing out is also ensured.

The inventive solution allows that a single first and a single second piston are present, so that only one ignition takes place with each full revolution.

However, the solution according to the invention leaves it without this associated with significant 'additional effort, to that two pairs of pistons, which are opposite in the radial direction

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are arranged, are present, so that two ignitions are present for a full revolution. Are accordingly then even with a full rotation there are twice the suction, compression and pushing out.

The solution according to the invention also allows that at a Rotation three or even four ignitions with corresponding suction processes, compression and expulsion are available. This is made possible by the adjustable relative movement of the second piston to the one with constant peripheral speed rotating first piston, as the later 'will be shown in detail.

Regarding the definition of the peripheral speed, it should be noted that that the first piston, seen over one or more revolutions, rotates at the same peripheral speed. this does not mean that this peripheral speed cannot be changed should be. The first piston can rotate at a peripheral speed of five thousand, for example Revolutions per minute or ten thousand or fifteen thousand Revolutions per minute. As a yardstick for the definition of "constant circumferential speed" it is stated that at a full revolution regardless of whether there are five thousand or fifteen thousand revolutions per minute, a constant peripheral speed available is. The second piston always has, regardless of whether it is in

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Overall also five thousand, ten thousand per minute or makes fifteen thousand or more revolutions, different circumferential speeds during one revolution, So when sucking in the peripheral speed 0, when compressing a peripheral speed, which in the end result is twice as great as the peripheral speed of the first piston, then again a peripheral speed on the working stroke of 0 and when pushing out a peripheral speed to compensate for this, which in turn is on average is twice as great as the peripheral speed of the first piston.

In a further embodiment according to the invention, it is proposed that that the first, with constant peripheral speed rotating pistons on an inner shaft and the second, with intermittent peripheral speed rotating piston is arranged on a surrounding outer shaft (hollow shaft). These coaxial waves result a simple structure with simple storage and a balanced torque curve, because these waves at the same time Can represent flywheels.

In a further embodiment according to the invention, it is proposed that that de.r first and second piston each have working surfaces lying in a radial plane and the

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first piston has a circumferential surface that extends over a Extends angular amount of about 90 °, the second piston has a circumferential surface that extends over an angular amount extends from about 30 ° and the back of the first piston to the outer circumference of the shaft carrying the piston approximately runs tangentially and the back of the second piston is parallel or almost parallel to the working surface of this piston runs parallel and both pistons are mirror images of the planes of their working surfaces. This particular one The three-dimensional shape of the two pistons enables their mutually facing working surfaces to rest against one another can or can be close to, but also their backs can come to the plant or approximate plant.

It should be understood that the above-described three-dimensional shape of the two pistons with respect to their working surfaces lying in the radial plane and also their backs are the basic spatial shape, with the work surfaces and the backs can receive special additional room shapes. So they do not need to be trained flat, but can in be slightly curved in order to improve the suction, the compression, but especially the expulsion. In Another embodiment according to the invention is proposed that the first piston is arranged on a sleeve which

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the inner shaft surrounds and is rotatably connected to this, the second piston is attached to a bushing which surrounds the outer shaft and is non-rotatably connected to it, one of the two bushings in the area of the cylinder space have the same outer diameter and the pistons protrude over their associated bushes on the front side, the front sides of the sockets touch each other and one face is provided with a circular ring seal.

The pistons are provided with associated seals which bear against the walls of the cylindrical housing. In Another embodiment according to the invention is proposed that the wave of the first, with constant peripheral speed rotating piston designed as an outgoing shaft is surrounded by a fixed sun gear, around which a planet gear rotates, which is attached to a cantilever arm that carries the first piston Shaft goes out, the planet gear is provided with an eccentric crank pin on which a connecting rod is mounted, which is connected to an eccentric pin which is attached to the shaft supporting the second piston. By this arrangement is at the same peripheral speed of the first piston the intermittent movement of the second Piston controlled.

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In another inventive embodiment, it is proposed that the inner shaft is hollow and is provided in the region of the rear sides of the piston with radially extending openings ₅ as
Air supply line to the rear of the piston is used. This proposal achieves air cooling of the piston and also of the cylinder wall. The air cooling according to the invention can also be used to compress the combustion air, which is then added to the combustion mixture via the inlet in the cylindrical casing, by the further measure that the rear sides of the pistons are designed as compressor working surfaces.

The inventive design of the rotary piston engine is thus designed in such a way that the working surfaces of the piston result in the intake, compression, the working stroke and the pushing out of the fuel mixture, while the backs of the two pistons serve as a compressor and
compress the combustion air. Since the combustion air serves to cool the walls of the cylinder and the pistons at the same time, it is additionally heated as compressed air, so that the performance of the rotary piston engine according to the invention is significantly increased.

In a further embodiment according to the invention, it is proposed that that the diameter of the fixed solar

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wheel or the circumference of the sun gear is twice as large as the diameter or the circumference of the planetary gear. By this solution it is achieved that the planetary gear is achieved by one revolution of the planetary gear around the sun gear turns twice. This solution is intended for the double existing in a cylindrical chamber Arrangement of the two opposite in the radial direction Pistons.

However, if the planet gear has the same diameter as the sun gear, then this arrangement is provided for only a single first and a single second piston. Provided the planet gear has a diameter which corresponds to a third of the sun gear, then triple first and second pistons are formed applied, over one revolution then three ignitions with corresponding assigned three aspirations take place, Consolidations and extensions.

It should be noted, however, that only two are advantageous in a housing opposite first and second pistons are present and, if an even higher power is to be provided, it is advisable to have several cylindrical chambers with corresponding double chambers in the axial direction to arrange first and second pistons.

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The invention is shown by way of example in the drawing. Show it:

Figure 1 in perspective and essentially

schematic representation of the overall view the rotary piston engine,

FIG. 2 shows the first and the second in a vertical section in a cylindrical housing KoIben,

Figure 3 essentially schematically and in a ver. vertical section in the radial plane in the cylindrical Housing the first and second piston in a single design,

Figure 4-15 vertical sections shown in the radial plane through the rotary piston engine at various Positions of the first and second pistons,

FIG. 16 shows the principle of the sun gear

with the planet gear to control the second piston,

FIG. 17 shows in principle the control of the second piston in relation to the first piston,

Figure 18-24 in a basic representation - 'the control of the second piston in relation to the first piston, '

FIG. 25 shows a basic representation of the arrangement of two interacting planet gears,

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Figure 26+ 26Α the first piston in vertical section

and in front view, FIG. 27 shows the second piston in vertical section

in radial plane,

FIG. 28 the second piston in vertical section,

FIG. 29 shows a vertical section through the entire engine.

Figure 1 shows the rotary piston engine 10, in its cylindrical Housing 11, consisting of the first side wall 12 and the second side wall 13 and the cylindrical Rotate jacket surface 14 pistons. First there is the Piston 16 attached to an inner shaft 15 with a piston 16 offset by 180 °, also arranged on shaft 15 Piston 16a, the special three-dimensional shape of which will be described later. On a coaxial outer shaft 17 is attached the second piston 18 and the opposite piston 18a. There is a cam on the outer shaft 17 19 with a pivot pin 20 eccentric to the shaft 17, which is surrounded by the bearing 21 of a connecting rod 22, which at its other end engages around the pin 24 a with a bearing 23, which is arranged eccentrically on a circular disk 24 which is firmly connected to a planet gear 25. The planet gear 25 is provided with teeth and meshes with a fixed sun gear 26 and is around its circumference

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emotional. The sun gear is attached to the stator 27. It surrounds the inner shaft 15. On the inner shaft is the Extension arm 28 attached to the planetary gear 25 and the disc via a pin 25a in connection with a bearing 24 wears. From this description it follows that the piston 16 attached to the inner shaft 15 or its counter-piston 16a, with constant rotation, carries the disk 24 via the arm 28, which disk is connected to the sun gear 25. The disk 24 has the aforementioned eccentric pin 24a, which with the rotation of the planetary gear 25 around the sun gear correspondingly rotates about the axis 25a. The arrangement of the planetary gear and the disc 24 with an eccentric pin 24a in connection with the connecting rod 22 and the eccentric pin 20 on the outer shaft 17 results in the control for the relative movement between the first piston 16 and the second piston 18, as will be described in detail later will be.

Figure 2 shows in a section essentially schematically that in the same way as shown in Figure 1, on the outer shaft 17 of the second piston 18 and on the inner shaft 15 of the first piston 16 is present. Is shown also the cylindrical housing with walls 12 and 13 and also extending in the radial plane to the aforementioned shafts the cylindrical wall 14, which is provided with a cooling channel29 for

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water cooling is provided.

According to FIG. 3, only one piston 16 is present on the inner shaft 15. Correspondingly, only a single second piston is present on the outer shaft 17. In this version, only one ignition according to one the intake operation is performed per revolution _s compression and pushing out. The pistons 17 and 18 are shown in a simple form with their flat working surfaces 30 and 31 and rear sides 32 and 33 running parallel to them.

An improved three-dimensional shape of the pistons 16 and 18 is shown in FIGS. 4 to 15, which also show the workflow. A rotary piston engine is shown with two pistons each, ie a double piston engine, so the respective opposing pistons 16, 16a and 18, 18a ₉ rotate in the indicated arrow direction 34 with the housing 14 stationary.

FIG. 4 shows that via the inlet 35, which has an opening in of the cylindrical wall 14 represents the combustion mixture is sucked in and the pistons 16 and 18 with their associated working surfaces 30 and 31 lie close to one another.

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FIG. 5 shows the position of the pistons 16 and 18 with respect to one another, in which the piston 16 in the indicated direction 34 around 30 ° is moved, but the piston 18 is here as its starting position has retained the designated position. As the piston 16 moves, the space increases between the working surfaces 30 and 31 of the two pistons, so that the mixture continues via the inlet opening 35 is sucked in.

Figure 6 shows the movement of the piston 17 by a further 30 °, i.e. overall from the initial movement, with the working surfaces 30 and 31 were in a horizontal plane by 60 °. The space between the work surfaces 30 and 31 continued to increase in size so that further suction took place.

According to FIG. 7, the piston 16 has made a rotation of 90 ° and the piston 18 has a rotation of approximately 40 ° carried out with the result that the working space between the work surfaces 30 and 31 has become smaller and the compaction of the mixture has started.

According to Figure 8, the piston 16 has performed a rotation of 120 ° and the piston 18 has a rotation of about 85 °, so that the piston 18 has not only followed the piston 16, but

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because he now has a greater peripheral speed than the piston 16 has started to overtake it with the result that the between the working surfaces 30 and 31 The existing space became smaller and the compression of the mixture increased. The compression is even stronger at the illustration according to Figure 9, in which the piston 16 a rotation of 150 ° and the piston 18 a rotation of approx. 130 ° so that the compression was further increased.

According to FIG. 10, the piston 16 has rotated through 180 °. The piston 18 has also performed a rotation of 180 ° so that it has caught up with the first piston 16. Here the maximum compress> n is available. The ignition, which is indicated in the form of the spark plug 36, takes place accordingly in this position. The outer peripheral surfaces of the pistons 16 and 18 cover the candle 36 afa ₀ so that it can only be effective within the gap or space between the two pistons. Therefore, the candle can be designed as a permanently glowing candle, so that no speed-dependent control of an ignition point is necessary, as is usual with other engines.

The position according to FIG. 10 is also the initial position for the second pair of pistons 16a and 18a and thus corresponds to

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the position according to Figure 4, because now between the work surfaces 30a and 31a the suction of the next mixture takes place. The process leading to Figures 4 to has been described, need not be described with respect to the pistons 16a and 18a, because he is in the same Way expires.

When the mixture is ignited, pressure is exerted on all sides. So on the working surface 30 of the piston 16 and 31 of the piston 18. A pressure is thus exerted on the piston 16, which moves it in the indicated arrow direction 34. Figure 11 shows the further movement of the Piston 16 by 210 °. The piston 18 has stopped, because it still has its turning position of 180 °. Also in the illustration according to FIG. 12, in which the piston 16 has been rotated by 210 °, the piston 18 has still retained its position of 180 °, so that the working stroke continues to take place.

According to FIG. 13, the piston 16 has performed a rotation of 270 °. The piston 18 has a rotation of approximately 220 ° carried out with the result that it follows the piston 16 with a peripheral speed, which in turn is larger than that of the piston 16, so that the existing between the working surfaces 30 and 31

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combustion chamber becomes smaller and the pushing out begins can.

According to FIG. 14, the piston 16 has rotated 300 ° and the piston 18 rotated approximately 260 °.

According to FIG. 15, the piston 16 has performed a rotation of 330 ° and the piston 18 a rotation of about 315 °, so that the combustion chamber has become so small that finally The combustion gases can be discharged via the outlet 37. As the piston 16 continues to rotate the new cycle is then carried out according to FIG. 4 with the suction.

Figures 4 to 15 show that two ignitions per revolution and accordingly also twice the suction, compression and pushing out takes place.

Figure 4 also shows that the inner shaft 15 is hollow and in the area of the pistons 16 and 16a with radial Bores 38 and 39 is provided so that the backs 40 and 41 and also the corresponding walls of the housing 14 are cooled with air introduced through the hollow shaft and the openings 38 and 39 mentioned will. Since the back of the surface 41 of the piston 18a is almost parallel to the working surface 31a and

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the rear surface 40 of the piston 18 with a circumferential extension of the piston 16 extends approximately tangentially from close to 90 ° to the outer circumference of the shaft 15, results as the illustration in Figures 4 to 15 shows, that during the rotation of the pistons 16 and 18 or 16a and 18a, formed by the rear sides 40 and 41 of the pistons, there are also compression spaces that change in volume. When the front work surfaces the piston 16 and 16a move away from each other, finds through the rear surfaces 40 and 41 of these Piston compresses the air supplied. This air supplied through the hollow shaft, which increases with increasing Volume of the space that is bounded by the back is sucked in, and by decreasing Volume is compressed on the back of the piston, can not only be used for cooling, but also as compressed air, which is then heated at the same time, the spaces between the working surfaces 30 and 31 of the pistons are fed. The engine according to the invention is thus at the same time due to the use of the rear sides of the pistons Compressor without the need for additional structural work or significant additional work. Figure 6 shows a line 42 which opens into the intake port 43 and serves to compress the through the rear sides of the pistons Bring air into inlet 35.

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The control device shown in FIG. 1 for the relative movement of the second piston 18 to the first piston 16 is initially to be explained with reference to FIG. According to the exemplary embodiment, the sun gear 26 has a radius of 5 cm, ie a diameter of 10 cm. The planet gear has a radius of 2.5 cm, ie the diameter of 5 cm. It can also be shown that the circumference of the sun gear 26 is twice as large as the circumference of the planet gear 25. The eccentric pin 24a of the disk 24 according to FIG. 1, but in principle also of the planet gear 25, is also shown in FIG. With the sun gear 26 stationary, provided that the planet gear is rotated in the indicated direction of arrow 44, the planet gear e'r, 3 rotates in the indicated direction of arrow 45. 16 shows graphically the sequence of movements with a position of the planet gear 25 relative to the sun gear 26 at a position of 45 ° in the indicated direction of rotation 44. It follows that here, since the circumference of the planet gear is half as large as that of the sun gear 26, that when the planet gear 25 moves in the direction indicated by 45 °, the pin 24a has performed a rotation of 90 ° about the axis 25a. If the planet gear 25 has covered a path extending over 90 ° around the circumference of the .Sonnenrades 26, then the pin 24a

ORIGINAL INSPECTED

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around the axis 25a accordingly by twice the angular amount, here 180 °. The further representations of the planet gear 25 and the position of the pin 24a can be understood from the drawings with regard to the preceding description. It can thus be seen that the pin 'Ma has received the starting position with a rotation of 180 °, here for example the distance to the center or circumference of the sun gear 26 as a reference value. This sequence of movements is used to control the outer pistons 18 and 18a supporting shaft 17 used. It will be explained further with reference to FIG. FIG. 17 shows in the upper area the movement of the planet gear 25 around the sun gear 26 with a rotation in the indicated arrow direction of 10 ° in each case and in the lower area of 30 ° in each case. First of all, it can be seen that, in accordance with FIG. 16, the center point of the pin 24a has the positions which are also shown in FIG. In the starting position, the center point of the pin 24 rests against the circumference of the sun gear. With a rotation of 90 ° it has the greatest distance to the circumference and with a further rotation of 90 ° it is in contact with the circumference again. It should be noted that this is illustrative and the pivot pin 24a must coincide in the starting position with the circumferential line of the sun wheel in practice not the center.

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Figure 17 shows that the centers of the pivot pin at a rotation of 0 ° to 60 ° on a circular line 46 shown in dashed line and thus a center point 47 is present for this circular line. That means that here with a movement of the planetary gear around the sun gear, the distance between the pin 28 and the pin 24a remains the same, so that the connecting rod 22 around the axis of the center 47 and the one there Pin 20 executes a movement in the indicated arrow direction 47a, but does not move cam 19 in the process, which is shown in Figure 17 in dashed lines. Provided that the planet gear 25 in the indicated arrow direction 44 is moved by more than 60 °, then the constant distance between the respective axis of the Pin 24a is present for pin 20, so that a movement or rotation of the cam 19 and over this the shaft 17 takes place.

The aforementioned sequence of movements should be based on the other Figures 18 to 24 are explained.

FIG. 17 shows the position of the connecting rod 22 when the gear position of the planet gear to the sun gear of 0 °, here the position of the planet gear in the upper zenith. FIG. 18 shows the position when rotated by 20 °.

ORIGINAL INSPECTED BAD ORIGINAL

Figure 19 of 40 ° and Figure 20 of 60 ° with the proviso that the cam 19 was not moved and thus the over the hollow shaft 17 connected · piston 18 and opposed piston 18a their starting position accordingly also after the Figures 4, 5 and 6 have retained, while the piston 16 and its opposing piston 16a with constant Have moved peripheral speed. From Figures 18, 19 and 20 it can be seen that the pin 24a along the circular line 46 described in relation to FIG. 17 in the indicated arrow direction 47a from the circumference of the sun gear moved away. Provided that the center of the shaft 17 and the pin 20 are connected to one another in an imaginary line then takes place in accordance with the movement on the circular line 46, a movement of the pin 24a in the direction outward. These relationships change if a little more than 60 ° has been rotated, because then according to the embodiment the center of the pin 24a migrates in the direction of the circumference of the sun gear or with it In other words, the aforementioned circular line 46 is no longer present. This then forces, as shown in FIGS 27 show the cam 19 to rotate about the axis of the shaft 17 with the result that the piston 18 also is rotated. While in the positions up to 60 °, the pivot points 24a away from the circumference of the sun gear

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were carried out, as shown in FIGS. 20, 24, with a rotation of more than 60 ° to 180 ° one to 180 ° increasing Approaching the periphery or towards the periphery of the sun gear with the result that thereby a rotation of the shaft 17 and correspondingly of the piston 18 connected thereto takes place at a greater speed takes place as the rotation of the shaft 15 with the piston 16, so that the second piston 18, which is stationary during suction and the working stroke, in the connection on that with constant peripheral speed rotating piston not only lags behind, but catches up with it again for the periods of standstill to catch up. The lag of the second piston 18 is thus shown in FIGS. It shows FIG. 24 shows this starting position corresponding to FIG. 4 or FIG. 10 with the proviso that with two pistons 16, 18 the movement cycle is completed in a range from 0 ° to 1.80 ° is, and therefore no further description of the rotation from 180 ° to 360 ° is required because the movement sequence there from 0 ° to 180 ° corresponds and also emerges from FIGS. 11 to 15.

Figures 16 to 24 show the control of the sequence of movements of the intermittently moved piston 18 to the rotating at a constant speed of rotation Pistons 16 and 16 explain the standstill in FIGS

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of the second piston 18 in the initial phase of suction and the initial phase of the explosion, with the planetary gear 25 rotating continuously.

It was also shown on the basis of FIG. 17 that during the explosion and thus the pressure exerted on the piston 18, which is directed in a direction opposite to its direction of rotation, but no braking or the like takes place because the force exerted via the connecting rod 22 via the joint 24a in the circumferential direction of the planetary gear 25 is directed and thus contributes to its rotation on the fixed sun gear 26.

FIG. 25 shows the improved solution that the inner shaft 15, which carries the cam 19, is articulated via the bolt 20 is connected to the connecting rod 22, via a bolt 24a not with the toothing on the circumference of the sun gear 26 meshing planetary gear 25 is connected, but with a further planetary gear 25b, which is via the cantilever arm 28 and a connecting piece 28a extending therefrom connected to the planet gear 25 and in engagement is because it is also provided with the same toothing. That of the piston 16a of Figure 17 at The pressure exerted by the cam 19 and the connecting rod 22 is stopped during the rotation shown in FIG

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of the planetary gear 25 there now on the second planetary gear 25b transmitted, which rotates in the direction indicated by the arrow 45b and thus the planetary gear 25, which is connected to the The sun gear meshes, rotates in the indicated direction 47, so that it rotates about the sun gear 26 in the indicated direction 44. The second planet gear 25b is not with the sun gear 26 in mesh, but the periphery of this second planet gear 25b has the periphery of the sun gear 26 a short distance.

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Figure 26 shows that the first constant peripheral speed per revolution rotating piston 16 with two, essentially radially protruding, to the Sealing strip *! "48 and 48a provided on the side surfaces which is also in the area corresponding to the sectional drawing shown in the radial plane according to FIG extend the outer circumferential surface and there sections represent of sealing strips 48b. At the same time there is an annular sealing strip 49.

FIG. 27 shows that, in the same way as the first piston 16, the second piston 18 also has radially protruding sealing strips 50 and 50a, which also extend over the circumference in a partial section 51. At the same time is an annular sealing strip 52 is present.

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FIG. 29 shows an exemplary embodiment of a motor in a vertical section. On the carrier 53 are on Bearings 54 and 55 are present on both sides, which carry the inner shaft 15. On the bearing housing 56 is over Screws 57 and 58 screwed on the sun gear 26, around which 'the planet gear 25 rotates, which via the shaft 25a with the arm 28 is connected, which carries the disc 24 with the eccentric pin 24a on which the connecting rod 22 is articulated is that on a bracket 19 with the pin 20. attached, which is connected to the outer shaft 17, which the second piston 18

which is connected to the outer shaft 17 via a key 59. The inner shaft 15 is via a wedge 61 connected to the first piston 16.

FIG. 29 also shows, like FIG Bushing 60, which is connected to the key 59 with the shaft 17, protrudes. The also stands in the same way Piston 16 protrudes by the amount of half its length beyond bushing 62 with which it is integral. The jack is over a wedge 61 connected to the shaft 15.Fig. 25,26,27 and show that the first piston 16 is thus arranged on a sleeve 62 which surrounds the inner shaft 15 and with this is rotatably connected, the second piston 18 on a ..

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Bush 60 is attached, which surrounds the outer shaft 17 and is rotatably connected to this, both sockets 60, 62 have the same outer diameter in the area of the cylinder space and the pistons 16, 18 have the same outer diameter associated sockets 62, 60 protrude at the end, the end faces of the sockets touch each other and at least one end face of a bushing is provided with an annular seal 49.

With 64, 65, 66, 67 lubricant channels are shown. 68 denotes the coaxial bore of the inner shaft, which has the radial air ducts 38 and 39, which have also been explained with regard to FIG. 4, so that the rear sides of the two pistons 16 and 18 are used for cooling the pistons, but as a compressor in a further stage so that compressed air can be supplied to the working surfaces of the pistons ..

The solution according to the invention also allows a simple change "of the duration of the intake or compression or of ^the explosion and the expulsion of the burnt gases with the following simple stipulation: If the cam 19 is lengthened according to the figure, this results in a longer standstill of the second Piston 18. This means at the same time that the subsequent acceleration is stronger because the second piston is seen over a total of 180 ° to 360 ° in each case

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18 has the same speed or number of revolutions as the he has the first KoI ben 16.

If, with a longer lever 19, the second piston 18 or piston 18a has a longer standstill phase, then will the suction phase and also the explosion phase are extended. At the same time, pushing out takes place at a later start and thus accelerated in the end phase. The increased Duration of the suction also leads to an improved or increased suction volume and therefore to an increased compression .

The solution according to the invention can also be adjusted the ignition point in a simple manner. It has already been stated that no spark plug with sparks should be used needs to find the exact time point of the compression or the position of the first two and second piston needs to be matched. But it should be noted here that even with the constantly glowing spark plug one Adjustment of the ignition point can be achieved in a simple manner that the fixed sun gear 26 using elongated holes by an angular amount that corresponds to the width of one tooth of the toothing, can be rotated. The housing that holds the glow plug could also be rotated a little.

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Finally, it should be noted that the solution according to the invention is not only applicable to engines according to the Otto principle, because a spark plug or glow plug is mentioned, rather the solution according to the invention can also be used
for engines based on the diesel principle, in which such
high compression takes place, which leads to auto-ignition.

- Expectations -

ι ^'38 _t

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Claims (14)

Expectations .) Rotary piston engine, characterized that in a rotationally symmetrical housing (12, 13, 14) with a cylindrical interior with a first shaft (15) lying in the axis of the rotary housing with a constant peripheral speed one designed as a first piston (16) , si ch in the radial direction extending portion of a disk with constant peripheral speed rotates and opposite on one also axial second shaft (17), a second, also designed as a piston (18), extends in the radial direction extending section of a disc with your first piston (16) with respect to different rotational speeds rotates in such a way that the piston (18) works on the four-stroke principle Motor stands still for suction, for compression at a higher peripheral speed than the first piston (16) rotates, then also comes to a standstill on the working stroke, and again at greater peripheral speed for pushing out as the first piston (16) rotates. 2. Rotary piston engine according to claim 1, characterized marked that the suction is about an angle of approx. 60 °, the compression over an angle of approx. 120 °, the working stroke over an angle of approx. 60 ° and it is pushed out over an angle of approx. 120 °. 3. Rotary piston engine according to claim 1, characterized characterized in that on the first shaft (15) opposite and in mirror image two first piston (16, 16a) and on the second shaft (17) opposite and in mirror image two second ones Pistons (18,18a) are present. 4. Rotary piston engine according to claims 1 to 3, characterized in that arranged in the axial direction of the shafts (15, 17) and on them further first and second pistons (16, 16a and 18 and 18a) are arranged in adjacent chambers are. 5. Rotary piston engine according to claims 1 to 3, characterized in that the first, with constant peripheral speed rotating piston (16) on an inner shaft (15) and the second with intermittent peripheral speed rotating piston (18) is arranged on an outer hollow shaft (17) surrounding the shaft (15). 6. Rotary piston engine according to claim 1 and one or more of claims 2 to 5, characterized in that the first and the second Pistons (16, 18) each have working surfaces (30, 31) lying in a radial plane and the first piston (16) has a circumferential surface that extends over an angular amount extends from approximately 90 °, the second piston (18) has a circumferential surface which extends over an angular amount of extends approx. 30 °, the rear side (40) of the first piston (16) to the outer circumference of the piston supporting Shaft (15) runs approximately tangentially and the back (41) of the second piston (18) to the working surface (31) of this piston runs parallel or almost parallel and the two pistons (16, 18) to the planes of their Work surfaces (30, 31) are designed in mirror image. 7. Rotary piston engine according to claims 1 to 6 _s, characterized in that the first piston (16) is arranged on a bushing (62) which surrounds the inner shaft (15) and is non-rotatably connected to this, the second piston (18 ) is attached to a bushing (60) which surrounds the outer shaft (17) and is non-rotatably connected to it, both bushes (60, 62) in the area of the cylinder space have the same outer diameter and the pistons (16,18) BATH ORIGSMAL protrude over their assigned sockets (62, 60) on the front side, the end faces of the sockets touch each other and at least one end face of a socket with a circular ring seal (49) is provided. 8. Rotary piston engine according to claim 1 and one or more of Claims 2 to 5, characterized in that the pistons with seals are provided and bear with these on the walls of the cylindrical housing. 9. Rotary piston engine according to claim 7, characterized characterized in that the piston by the amount of half the length over the associated socket protrude. 10. Rotary piston engine according to claims 1 to 9, characterized in that the shaft (15) of the first, with constant peripheral speed rotating piston (16) designed as an outgoing shaft and from a fixed sun gear (26) is surrounded, around which one attached to a cantilever arm (28) of the shaft (15) carrying the first piston (16) Planet gear (25) revolves with an eccentric Crank pin (24a) is provided on which a connecting rod (22) is mounted, which with a pin (20) on a cam (19) is articulated, which is attached to the shaft (17) carrying the second piston (18). 11. Rotary piston engine according to claim 10, characterized - characterized in that the connecting rod (22) has a crank pin (24) with a second planetary gear (25b) is connected, the outer circumference of which is at a small distance from the outer circumference of the sun gear (26), this second planet gear (25b) is connected to the planet gear (25) via a cantilever arm (28) and with meshes with this planet gear (25), the planet gear (25) in turn meshing with the sun gear. 12. Rotary piston engine according to claims 1 to 11, characterized in that the inner shaft (15) is hollow and in the region of the piston (16, 18) with extending in the radial direction openings (38, 39) is provided and as an air supply line the piston (16, 18) serves to the rear sides (40, 41). 13. Rotary piston engine according to claim 12, characterized g e k e η η ζ e i ch η e t that the back sides (40,41) - 6 BATH ORIGIN the pistons are designed as compressor working surfaces. 14. Rotary piston engine according to claims 1 to 10, characterized characterized in that the diameter of the fixed sun gear (26) or the circumference of the sun gear is double is as large as the diameter or the circumference of the planetary gear (25). COPY