EP1597456A2

EP1597456A2 - Rotary piston machine with an oval rotary piston guided in an oval chamber

Info

Publication number: EP1597456A2
Application number: EP04714747A
Authority: EP
Inventors: Boris Schapiro; Lev Levitibn; Naum Kruk
Original assignee: "RKM-Rotationskolbenmaschinen" GbR vertr durch Herrn Dr Boris Schapiro; RKM ROTATIONSKOLBENMASCHINEN G
Current assignee: Excursion Ltd
Priority date: 2003-02-27
Filing date: 2004-02-26
Publication date: 2005-11-23
Anticipated expiration: 2024-02-26
Also published as: WO2004076819A3; RU2344296C2; US7117840B2; CA2517318A1; RU2005129640A; US7866296B2; WO2004076819A2; CA2517318C; US20070089701A1; DE10308831B3; RU2008133156A; JP2006519330A; KR20050116132A; KR101109422B1; RU2476696C2; EP1597456B1; US20060032475A1; JP4461138B2

Abstract

A rotary piston machine comprising a prismatic chamber (12) disposed in a housing (10), the cross-section of said chamber being oval-shaped. A rotary piston (22) can move in the chamber (12), the cross-section of said piston also being oval-shaped. The order of the oval of the chamber (12) is lower than the order of the oval of the rotary piston (22). The rotary piston (22) rotates alternately in successive movement sections around various axes of rotation, respectively from one stop position to the next. During rotation, the rotary piston is adjacent to the inner wall of the chamber (22) in each position, forming two working chambers (80,82). The rotary piston (22) comprises an opening with inner toothing (56).The inner toothing (56) engages with a toothed arrangement for driving the rotary movement. The opening (36) is, mathematically speaking, essentially similar to the rotary piston (22). The planes of symmetry (50,52,54) of the opening (36) coincide with those of the rotary piston (22). The toothed arrangement comprises a pair of shafts (70,72) which are fixed to the housing and provided with external toothing (74,76) which engages with the inner toothing (56) of the opening (36). In each movement section, one shaft (e.g. 70) is respectively arranged in the region of a section (28) of the opening which has a smaller radius of curvature and the other shaft (72) is arranged in the region of a section (46) having a higher radius of curvature. The shafts are actively interchangeable in successive movement sections.

Description

Rotary piston machine with an oval rotary piston guided in an oval chamber

The invention relates to a rotary piston machine with a prismatic chamber formed in a housing, the cross section of which forms an oval, and a rotary piston which is movable in the chamber and whose cross section also forms an oval, the order of which deviates from the order of the oval forming the cross section of the chamber. wherein the rotary piston rotates alternately in successive movement sections about different axes of rotation from one stop position to the next and, when it rotates in any position, rests against the inner wall of the chamber to form two working spaces, and with an internal toothing opening in the rotary piston, the ' Internal toothing with a toothing arrangement for the input or output of the rotary movement is engaged.

In mathematics, an "oval" is a non-analytical, closed flat convex

Figure composed of arcs. The arcs are set up continuously and differentially. The curve is continuous at the points where the arcs connect. The tangents of the two adjacent arcs also coincide there. The curve can be differentiated. At the points where the arcs connect with different radii of curvature, the second derivative - which determines the curvature - makes a jump. The oval consists of alternating circular sections with a first, smaller, and a second, larger radius of curvature. The order of the oval is determined by the number of pairs of circular sections with the first and the second radius of curvature. A second-order oval or bi-oval is "ellipse-like" with two diametrically opposite circular arcs of smaller diameter, which are connected by two circular arcs of larger diameter.

Rotary piston machines of the type mentioned are known.

US 3 967 594 A and US 3 006 901 A show a rotary piston machine with an oval piston in an oval chamber. The cross section of the piston is bioval. This bi-oval piston is movable in a tri-oval chamber. In these known rotary piston machines, complex gears are provided in order to transmit the rotary movement of the rotary piston to a shaft.

DE 199 20 289 CI also describes a rotary piston machine in which the cross section of a prismatic chamber formed in a housing is tri-oval with continuously and differentially adjoining first and second arcs of alternating a smaller radius of curvature and a larger radius of curvature. A rotary piston with a bi-oval cross-section is guided in the chamber. The bi-oval cross section of the rotary piston is alternately first and second

Circular arcs with the smaller or larger radii of curvature of the tri-oval cross-section of the chamber are formed, which again connect continuously and differentially to one another. In the tri-oval chamber, the bi-oval rotary piston carries out the movement cycles described above with jumping instantaneous axes of rotation. The movement of the rotary piston is tapped there in a very simple way: one

The shaft extends centrally through the tri-oval chamber, i.e. along the intersection of the symmetry planes of the chamber. The shaft carries a pinion. The rotary piston has an oval opening with internal teeth. The long axis in the cross section of the opening extends along the short axis of the bi-oval cross section of the rotary piston. The pinion constantly meshes with the internal toothing.

In the known rotary piston machines, a housing forms a prismatic chamber, the cross section of which is such an oval of odd order, for example a Third-order oval. The chamber forms cylindrical inner wall sections alternating with the first, smaller and the second, larger radius of curvature. In such an oval of third (fifth or seventh and higher) order, a rotary piston is movable, which in cross section forms an oval whose order is one less than the order of the oval of the chamber. The oval used for the rotary piston has a double symmetry, even if it has a higher order, ie it is mirror-symmetrical with respect to two mutually perpendicular axes. This rotary piston has two diametrically opposed cylindrical jacket sections whose radius of curvature corresponds to the smaller (first) radius of curvature of the oval of the chamber. If the rotary piston forms an oval in cross section, the second, larger radius of curvature of this oval is equal to the second radius of curvature of the oval forming the chamber. In a certain movement section, the rotary piston lies with a first of these cylindrical jacket sections in a complementary cylindrical inner wall section of the chamber, which has the same smaller radius of curvature. With the second, diametrically opposite cylindrical casing section, the rotary piston slides on the opposite cylindrical inner wall section of the chamber, which has the larger radius of curvature. In this way, two working spaces are formed by the rotary piston in the chamber, one of which increases in size and the other becomes smaller as the rotary piston rotates. The

The rotary piston rotates about a current axis of rotation. This instantaneous axis of rotation coincides with the cylinder axis of the first cylindrical jacket section. This current axis of rotation therefore has a defined position relative to the rotary piston. In this movement section, the instantaneous axis of rotation of course also corresponds to the cylinder axis of the cylindrical inner wall section which is fixed to the housing and has a smaller radius of curvature in which the rotary piston rotates. This rotation continues until the second cylindrical jacket section of the rotary piston reaches a stop position. In this stop position, the second cylindrical jacket section lies in the lower wall section of smaller diameter adjoining the opposite inner wall section with a larger radius of curvature.

A further rotation of the rotary piston around the current pivot point is not possible. The current axis of rotation therefore jumps for the next one Movement section in a different position, namely the cylinder axis of the second cylindrical jacket section. This new momentary axis of rotation is also in a defined position relative to the rotary piston. In the next movement section it corresponds to the cylinder axis of the cylindrical inner wall section, in which the second cylindrical jacket section of the rotary piston now rotates. In this movement section, the “first” cylindrical jacket section slides again on the opposite inner wall section with a larger radius of curvature.

In such a rotary piston machine, the rotary piston always rotates in the same direction of rotation but alternately around different instantaneous axes of rotation, the

"Jump" axes of rotation after each movement section. Two such instantaneous axes of rotation are defined in relation to the rotary piston, namely by the cylinder axes of the diametrically opposite cylindrical jacket sections. Relative to the housing and the chamber formed in it, the current axis of rotation jumps between the "corners" of the oval, ie the cylinder axes of the

Inner wall sections with a smaller radius of curvature.

With each movement section, the volume of one work area increases to a maximum value, while the volume of the other work area decreases to a minimum value. Ideally, if the rotary piston is also in the

If the cross-section forms an oval, the volume of the work area increases from practically zero to the maximum value or decreases to practically zero. Such a rotary piston engine can be used as a two-stroke or four-stroke internal combustion engine (with internal combustion) or as an external combustion engine, e.g. Steam engine. But it can also be used as an air pressure motor

Hydraulic motor or work as a pump.

In DE 199 20 289 CI, a rotary piston, the cross section of which is an oval of the second order, can be moved in a chamber whose cross section forms an oval of the third order. A single output shaft extending centrally through the chamber serves to tap the movement of the rotary piston. The output shaft protrudes through an oval opening in the rotary piston and carries a pinion. The pinion meshes with a toothing on the inside of the opening. In the known rotary piston machines, the order of the oval defining the chamber is in each case one greater than the order of the oval which forms the cross section of the rotary piston. A bi-oval rotary piston is guided in a tri-oval chamber. The current axes of rotation of the

Rotary piston in the stop positions relative to the rotary piston only between two positions, relative to the housing but between at least three positions. The rotary piston with the small radius section translates along the large radius section along the inner wall of the chamber. This can lead to sealing problems in the sealing between the work rooms

Chamber drove. Another problem arises from the fact that, in each working cycle of the rotary piston machine, successively more than two working spaces are formed, which move around along the inner wall of the housing.

The invention has for its object to improve the seal between the working spaces of the chamber in a rotary piston machine of the type mentioned.

The invention is further based on the object in the stop positions of the rotating body in a simple manner, a closed kinematics with clear

To ensure movement of the rotary piston.

For this purpose, the invention is specifically based on the object of reducing the number of instantaneous axes of rotation occurring in relation to the housing.

Finally, the invention is based on the object of designing a rotary piston machine of the type mentioned at the outset in such a way that only two alternatingly enlarging and reducing work spaces occur which are arranged opposite one another in fixed angular positions with respect to the housing.

According to the invention, these objects are achieved in that the order of the oval of the chamber is one less than the order of the oval of the rotary piston, the breakthrough is essentially mathematically similar to the rotary piston, the Levels of symmetry of the opening coincide with those of the rotary piston, and the toothing arrangement has a pair of shafts provided with external toothing and fixed to the housing, the outer toothing of which engages with the inner toothing of the opening, with one shaft in each area of a section of the opening with a smaller one Radius of curvature and the other shaft is arranged in the region of a section with a larger radius of curvature and the shafts interchange their roles in successive movement sections.

Surprisingly, you get a clear guidance of an oval in cross section

Rotary piston in an oval chamber with the formation of working spaces which are sealed off from one another, even if, in contrast to the prior art, the rotary piston has a higher order of oval than the chamber, e.g. a tri-oval rotary piston rotates in a bi-oval chamber. The rotation takes place around one of two momentary axes of rotation, which are fixed to the housing

Waves are formed. The axes of rotation have gears or external gears. which are in engagement with an internal toothing of an essentially oval opening in the rotary piston. One of the shafts sits in an area of the smaller radius of curvature of the oval opening, e.g. almost in a "corner" of the "arch triangle" forming the breakthrough. The other shaft is in engagement with the opposite area of the internal toothing with the larger radius of curvature, that is to say the opposite side of the triangular arch.

In a stop position, in the case of a rotary piston machine with a bi-oval chamber and a tri-oval rotary piston, the rotary piston with two adjacent regions with a larger radius of curvature and the region in between with a smaller radius of curvature bears against the inner wall of the chamber. When the rotary piston comes into such a stop position, the other shaft also sits in a corner of the arc triangle. The further rotation of the rotary piston in the same direction of rotation then takes place around the first-mentioned shaft. Here, too, the axes of rotation jump when a stop position is reached. However, this jumping takes place between two axles fixed to the housing, namely between the axes of rotation of the two shafts. In general, the following applies: In the case of a 2n oval chamber, the rotary piston guided therein has the order 2n + l. In the stop positions, the rotary piston with n + 1 "sides" then fits positively against the inner wall of the chamber, while in each case n "sides" limit the working chamber which then has its maximum expansion. Two working spaces are formed on opposite sides of the housing.

In the stop positions, the kinematics of the rotary piston in the chamber are not complete. Instead of a further rotary movement, e.g. by introducing a pressure medium into the work space, which is minimized in volume, or by igniting a fuel mixture, a transverse force occurs which leads to jamming of the

Rotary piston leads in the chamber. In order to solve this problem and to obtain a closed kinematics, speed-regulating means are provided in a further embodiment of the invention, by means of which, when a stop position is reached for that shaft, the external toothing in the previous movement section with the internal toothing in the region of the larger one

Radius of curvature was engaged, a lower speed can be enforced than for the other shaft. This ensures that the rotary piston continues to rotate in the intended manner around the shaft which is forcibly rotating at a lower speed. This forced speed setting only needs to be carried out briefly in each case until the rotary piston has turned out of the stop position. The forced

Speed can be specified in that one of two shafts fixed to the housing is braked by braking means, which is structurally simple to accomplish.

On one side, a peripheral portion of the rotary piston rotates relatively slowly on a peripheral portion with a large K-radius of curvature of the inner wall of the chamber.

The slow movement reduces the sealing problems. On the opposite side, a peripheral portion of the rotary piston with a large radius of curvature slides on such a peripheral portion of the inner wall. This results in a large sealing surface.

The two shafts rotate alternately at lower and higher speeds. By means of a differential or a freewheel, a constant speed of rotation of an input or output shaft coupled to the two shafts can be provided. Embodiments of the invention are explained below with reference to the accompanying drawings.

Fig.l shows a cross section of a rotary piston machine with two shafts, a rotary piston, the cross section of which forms an oval of the third order, is guided in a chamber, the cross section of which is an oval of the second order.

Fig.2 is a representation similar to Fig.2 and shows the rotary piston in one

Stop position.

Figure 3 is a representation similar to Figure 2 and shows the rotary piston during the next movement section.

4 shows a cross section of a rotary piston machine with two shafts, a rotary piston, the cross section of which forms a fifth-order oval, being guided in a chamber, the cross-section of which is an fourth-order oval.

4A shows a modification of the arrangement according to FIG.

5 shows a cross section of a rotary piston machine with two shafts, a rotary piston, the cross section of which forms a seventh-order oval, is guided in a chamber, the cross section of which is an oval sixth

Is okay.

Fig. 6 is a schematic representation of the speed regulating means.

7A is a schematic, enlarged representation of the seal in a

Rotary piston machine of the type shown in Figures 1 to 5, wherein the seal between a sealing strip and a Circumferential portion of the rotary piston with a smaller radius of curvature takes place.

7B is a schematic, enlarged representation of the seal in a rotary piston machine of the type shown in FIGS. 1 to 5, the seal between a sealing strip and a

Circumferential portion of the rotary piston is carried out with a larger radius of curvature.

FIG. 8 shows a detail of the rotary piston machine from FIG. 4A on an enlarged scale.

Figure 8 A shows the detail of Figure 8 on a further enlarged scale.

In Fig.l, 10 denotes a housing. A chamber 12 is formed in the housing 10. The cross section of chamber 12 forms a second order oval or is "bioval". The cross section of the chamber 12 is accordingly formed by two circular arcs 14 and 16 of a relatively small radius of curvature and alternately between two circular arcs 18 and 20 of a relatively large radius of curvature. The arcs are continuous and differentiated.

A rotary piston 22 is guided in the chamber 12. The cross section of the rotary piston 22 forms a third-order oval or is tri-oval. Accordingly, the circumference of the cross section consists of three pairs, each of a circular arc of relatively My radius of curvature 24, 26 and 28 and a circular arc of relatively large

Radius of curvature 30, 32 and 34 formed. The circular arcs of small and large radius of curvature alternate and are also continuous and differentiable. The small radii of curvature of the rotary piston 22 are equal to your radii of curvature of the chamber 12, and likewise the large radii of curvature of the rotary piston 22 are equal to the large radii of curvature of the chamber 12

Chamber 12. The cross section of chamber 12 resembles an ellipse, although it is not an ellipse at the moment. The cross section of the rotary piston 22 is similar to an arc triangle with rounded corners. The rotary piston 22 has a central opening 36. The cross section of the opening 36 also forms a third-order oval. This third-order oval is formed by three circular arcs with a relatively small radius of curvature 38, 40 and 42 and three circular arcs 44, 46 and 48 with a relatively large radius of curvature. The

Arcs 38, 40 and 42 with a small radius of curvature and the arcs 44, 46 and 48 with a large radius of curvature adjoin each other alternately and continuously and differentially, so that an oval is formed like an arc triangle with rounded ends. The planes of symmetry 50, 52 and 54 of the opening 36 coincide with the planes of symmetry of the rotary piston 22.

The opening 36 has an internal toothing 56. This internal toothing 56 has three concave-arched toothed strips 58, 60 and 62, essentially along the circular arcs 44, 46 and 48 of large radius of curvature. Between these concave-arched toothed racks 58, 60 and 62 are small in the area of the circular arcs

Radius of curvature provided convex-arc-shaped (or possibly straight) toothed strips 64, 66 and 68.

Through the opening 36, two parallel shafts 70 and 72 with gears 74 and 76 extend. The axes of the shafts 70 and 72 lie in the through

Circular arcs 18 and 20 running plane of symmetry 77 of the chamber 12. The gear wheel of the one shaft, in FIG. 1 the gear wheel 74 of the shaft 70, sits in the "corner of the arc triangle", i.e. in the region of the circular arc 38 of small radius of curvature and is in engagement with the internal toothing 56 in a manner to be described. The gear wheel of the other shaft, in FIG. 1 the gear wheel 76 of the shaft 72, is in engagement with the opposite concave-arch-shaped toothed rack, in FIG. 1 the toothed rack 60.

The rotary piston 22 divides the bi-oval chamber 12 into two working spaces 80 and 82. In FIG. 1 the rotary piston machine is shown schematically as

Internal combustion engine shown with internal combustion. Accordingly, an inlet valve 84 and 86 and an outlet valve 88 and 90 are shown for each working space 80 and 82. Furthermore, there is a work space 80 and 82, respectively Brermkarnmer 92 or 94 with a spark plug or an injection nozzle 96 or 98. The working spaces 80 and 82 with the valves and spark plugs or injection nozzles are symmetrical to the plane of symmetry extending through the circular arcs 14 and 14 of the cross section with a small radius of curvature. This is only a schematic representation.

In the regions 18 and 20 of the large radii of curvature, pairs of mutually adjacent sealing strips 100A and 100B or 102A and 102B are provided on the housing. The sealing strips 100A and 100B or 102A and 102B are symmetrical to that through the circular arcs 18 and 20 of large cross-section

Radius of curvature extending plane of symmetry.

FIG. 7A shows the sealing strips 100A and 100B at a position in the region of the transition from the smaller radius of curvature rj of the outer surface of the rotary piston 22 on the right in FIG. 7A to the region of the larger radius of curvature r _{2 of} this outer surface on the left in FIG. 7A. The sealing strip 100A has a concave-cylindrical inner surface, the radius of curvature of which corresponds to the larger radius of curvature r ₂ . The sealing strip 100B has a concave-cylindrical inner surface whose radius of curvature corresponds to the smaller radius of curvature r _x . It can be seen that the inner surface of the sealing strip 100A is in the region of the radius of curvature r _{2 of} the

Rotating piston 22 abuts the complementary surface of the rotating piston 22. In the region in which the radius of curvature of the surface of the rotary piston 22 is smaller, namely r _t , a wedge-shaped gap 100C is formed between the sealing strip 100A and the rotary piston 22 and the inner surface of the sealing strip 100A. The sealing strip 100B has a concave-cylindrical

Inner surface whose radius of curvature corresponds to the smaller curvature radius r _t . It can be seen that the inner surface of the sealing strip 100B lies tightly against the complementary surface of the rotary piston 22 in the region of the radius of curvature τ _{t of} the rotary piston 22. In the area in which the radius of curvature of the surface of the rotary piston 22 is larger, namely r ₂ again, a wedge-shaped gap 100D is formed on the right in FIG. 7A between the sealing strip 100B and the rotary piston 22 and the inner surface of the sealing strip 100A. In the transition area shown, both sealing strips are each on one Part of the inner surface in flat contact with the outer surface of the rotary piston, so that a surface seal is guaranteed.

7B shows in a similar manner the seal in the area of the transition from the large radius of curvature r ₂ to the smaller radius of curvature r ,. If the pair of sealing strips 100A and 10B abuts only on a region of the rotary piston 22 with a large radius of curvature r ₂ or only on a region with a small radius of curvature, either the sealing strip 100A or the sealing strip 100B, with the entire inner surface in each case, ensures a flat contact and sealing.

The arrangement described works as follows:

The rotary piston 22 rotates counterclockwise in Fig.l. The rotary piston 22 rotates about the shaft 70 and slides at a low speed on the inner wall of the chamber 12 in the region of the large radius of curvature. The axis of the

Wave 70 passes through the center of curvature of the circular arc 24 of small radius of curvature. The circular arc 24 touches the circular arc 18 of the cross section of the chamber 12. The opposite region of the circumferential surface of the rotary piston 22 with the large radius of curvature corresponding to the circular arc 32 lies against the region of the inner wall of the chamber 12 corresponding to the circular arc 20.

This area of the inner wall has the same radius of curvature as the adjacent area of the outer surface of the rotary piston. So there is a form-fitting, flat system. During the rotary movement, this area of the lateral surface of the rotary piston slides on the corresponding area of the inner wall.

The working space 80 increases while the working space 82 shrinks. The shaft 70 is rotated relatively slowly, while the shaft 72 rotates relatively quickly.

This movement continues until the right stop position in Fig. 2 is reached.

Then the area of the circumferential surface of the rotary piston corresponding to the circular arc 28 lies in the area of the inner wall of the chamber 12 which corresponds to the circular arc 16. Both areas have the same, namely the small one Radius of curvature. The regions of the circumferential surface of the rotary piston which correspond to the circular arcs 32 and 34 with the large radius of curvature lie against the regions of the inner wall of the chamber 12 which correspond to the circular arcs 18 and 20 of the cross section. The radii of curvature are the same again. The volume of the working chamber 82 is thus reduced to zero apart from the brake chamber 94, while the working chamber 82 has its maximum volume. The shaft 72 with the toothed wheel 76 then lies in the opening 36 in the area which corresponds to the circular arc 40, that is to say in the lower left "corner" of the triangle. The rotary piston 22 can no longer rotate about the axis of the shaft 70 as the current axis of rotation.

This position is shown in Fig.2.

With a further rotation, e.g. is caused by ignition of fuel in the combustion chamber 94 in an internal combustion engine or by introducing a working medium into the working chamber 82, the current axis of rotation jumps into the axis of the shaft 72. The rotary piston continues to rotate counterclockwise, but now around the shaft 72.

The further course of motion is then related to the new current axis of rotation as described above with reference to the axis of the shaft 70 as the current axis of rotation.

When the rotary piston 22 rotates, successive movement sections occur. Each movement section runs from one of the described stop positions to the next. In each movement section, a work space increases, e.g. 80, from zero to a maximum, while the other workspace is reduced from the maximum to zero. In the next movement section, it is the other way round: the work space 82 increases from zero (FIG. 2) to a maximum, while the work space 80 shrinks again

(Fig.3). The kinematics is not clear in the position of FIG. Each of the two shafts could define a current axis of rotation with its axis. If, for example, a force is exerted to the left on the rotary piston 22 by a working medium introduced into the working space 82, this force could possibly lead to a translatory movement in the horizontal direction in FIG. 2 instead of a rotation of the rotary piston 22 about a momentary axis of rotation. This would wedge the rotary piston 22 in the chamber 12.

If this danger exists, it can be countered by briefly forcing a lower rotational speed of the shaft 72 than the rotational speed of the shaft 70 in the position of FIG. 2 by speed regulating means. The rotary piston 22 is then forced to move around this shaft 72 to rotate, while the other shaft 70 allows a rolling of the concave-arched rack 62 on the gear 74.

This is shown schematically in Figure 6. Sensors 140 detect the position of the

Rotary piston in 22 in chamber 12. The sensors signal when the rotary piston has reached a stop position. A control 142, which is acted upon by the signals from the sensors, then controls devices 144 and 146, by means of which, depending on which stop position has been reached, rotational speeds of shaft 70 and shaft 72 are briefly predetermined. It will then e.g. the shaft 70 has a low speed and the shaft 72 has a higher speed or vice versa. In the simplest case, the devices 144 and 146 can be braking devices, which act alternately briefly on the shaft 70 or the shaft 72 in the stop positions, while the other shaft remains unrestrained.

The radii of the partial circles of the gearwheels correspond essentially to the small radii of curvature of the second-order oval forming the opening 36. If the internal toothing 56 would continuously follow the oval of the opening 36, the gearwheels would be caught in the end positions of the rotary piston 22. The "corners" of the "triangle" could not roll over the gears. For this reason, the concave-arched toothed strips in the region of the circular arcs 38, 40, 42 with a small diameter are connected by short straight or convex-arched toothed strips 64, 66 and 68, respectively. The convex-arched toothed racks 64, 66 and 68 allow the rear toothing 56 and thus the rotary piston 22 to roll on over these areas. They are dimensioned such that in the stop positions one of the concave-arched toothed strips 58, 60 or 62 comes into engagement with the gear 74 or 76 immediately after the engagement of the gear 74 or 76 with the previous toothed strip 62, 58 or 60 is released has been. In this way, each gear is constantly in engagement with one of the concave-arched toothed racks 64, 66 or 68. The short convex-arch-shaped or straight toothed strips ensure a transition without interrupting the form fit but also without blocking.

4 shows a rotary piston machine with a chamber 104, the cross section of which forms a fourth-order oval 106. A rotary piston 108 is guided in the chamber 104, the cross section of which forms a fifth-order oval 110. Here too, the rotary piston 108 has an opening 112 whose shape forms a fifth-order oval 114. The axes of symmetry of the rotary piston 108 and the opening 112 coincide. The opening 112 has an internal toothing 116. The internal toothing 116 is in engagement with two gear wheels 118 and 120. The gear wheels 118 and 120 are seated on two shafts 122 and 124 fixed to the housing. The axes 126 and 128 of the shafts 122 and 124 lie in a plane of symmetry of the chamber 104.

The rotary piston 108 divides the chamber into two working spaces 130 and 132, one of which enlarges and the other decreases as the rotary piston rotates.

The workflow is similar to the workflow of the execution from Fig.l to 3. The

Rotary piston 108 rotates e.g. about the axis 126 of a shaft 122 up to a stop position. Then the current axis of rotation jumps into the axis 128 of the other shaft 124. The rotary piston rotates further about this axis counterclockwise from FIG. 4 to the next stop position. The sequence of movements between two successive stop positions is a "movement section".

In each movement section, the working space 130 increases from zero to a maximum and the working space 132 decreases from a maximum to zero or vice versa. The workspaces are always on both sides of axes 126 and 128 of the plane of symmetry containing waves 122 and 124. They do not wander around the chamber.

In Fig. 4 valves and spark plugs or injection nozzles are shown (schematically) for each work area.

Figure 4A shows a rotary piston machine similar to that of Figure 4. Corresponding parts have the same reference numerals as there. Details of the rotary piston machine of Figure 4A are shown on an enlarged scale in Figures 8 and 8A.

In the rotary piston machine of FIG. 4A, an injection nozzle is designated by 150. The injection nozzle 150 protrudes into a combustion chamber 152. This combustion chamber is dimensioned and designed in such a way that the fuel injected essentially only burns in the combustion chamber. Only the expanding combustion gases then enter the expanding work area. The injection can be metered as a function of time or as a function of the rotation of the rotary piston so that it is adapted to the change in volume of the working space 130 or 132. No flame front then appears in the work area. The spreading of flame fronts in an expanding work space causes problems in known rotary piston machines.

In the embodiment of Figure 8 and 8A, the combustion chamber 152 to a kugelkalottenf ^'shaped recess of the housing, to which a kegelstumpffδrmiger, to the processing space tapering space 156 is connected. The space 156 is formed in an insert 158 which is threaded into an insert

Recess of the wall of the working space 130 or 132 is screwed in. The combustion chamber 152 is closed off by a grid or network 160. The injection nozzle 150 runs out into a cone rounded off at the tip, the injection taking place via nozzle openings in the jacket of this cone.

The described arrangement of the injection nozzle in a combustion chamber, such that the combustion takes place essentially only in the Brermkammer and flame fonts in the work rooms can be avoided, can also be used with other machines, for example with reciprocating piston machines.

5 shows a rotary piston machine, in which a rotary piston, the cross section of which forms an oval of the seventh order, is guided in a chamber whose

Cross section is a sixth-order oval. The structure and function are, apart from the order of the ovals, similar to that of the embodiment in Fig. 4. Corresponding parts are provided with the same reference numerals as in FIG. 4 but with the addition "A".

Claims

claims

Rotary piston machine, with a prismatic chamber (12) formed in a housing (10), the cross section of which forms an oval of circular arcs (14, 16; 18, 20) of alternately smaller and larger radius, and a rotating piston movable in the chamber (12) (22), the cross section of which also forms an oval with the same alternately smaller and larger radii, the order of which deviates from the order of the oval forming the cross section of the chamber (22), the rotary piston (22) alternating in successive movement stages around different axes of rotation rotates from one stop position to the next and, when it rotates in any position, bears against the inner wall of the chamber (12) to form two working spaces (80, 82), and one with one

Internal toothing (56) provided opening (36) of the rotary piston (22), the inner toothing (56) of which engages with a toothing arrangement (74, 76) for the drive or output of the rotary movement, characterized in that

(a) the order of the oval of the chamber (12) is one less than the order of the oval of the rotary piston (22),

(b) the aperture (36) is essentially mathematically similar to the rotary piston (22), the planes of symmetry (50, 52, 54) of the aperture (36) coinciding with those of the rotary piston (22), and

(c) the toothing arrangement (56) has a pair of shafts (70, 72) provided with outer toothing (74, 76) and the outer toothing (74, 76) of which is engaged with the inner toothing (56) of the opening (36) , with the one in each movement section

Shaft (eg 70) in the region of a section (38) of the opening (36) with a smaller radius of curvature and the other shaft (72) in the region of a section (46) with a larger radius of curvature and the Waves (72, 74) swap roles in successive movement sections.

2. Rotary piston machine according spoke 1, characterized in that speed-regulating means (142, 144, 146) are provided, by means of which

Reaching a stop position for the shaft (70 or 72) whose outer toothing (74 or 76) rolled in the previous movement section on the inner toothing (56) of the opening (36) in the region of a larger radius of curvature, a lower speed can be forced than for the other Shaft (72 or 70) around the axis of which the rotary piston (22) rotated in the previous movement section.

3. Rotary piston machine according to claim 2, characterized in that by the speed regulating means when reaching a stop position that shaft (70 or 72), the external toothing (74 or 76) in the previous movement section on the internal toothing (56) in the region of a larger radius of curvature unrolled, is temporarily braked.

4. Rotary piston machine according to one of claims 1 to 3, characterized in that pairs of side-by-side sealing strips with concave-cylindrical inner surfaces are provided in the inner wall of the chamber for sealing between the working spaces, the radius of curvature of one inner surface being equal to the smaller radius of curvature (η ) and the radius of curvature of the other sealing surface is equal to the larger radius of curvature (r ₂ ) of the outer surface of the rotary piston (22).

5. Rotary piston machine according spoke 4, characterized in that two pairs of sealing surfaces are arranged diametrically opposite symmetrically to the plane of symmetry of the housing (10) going through the axes of the shafts (70, 72). Internal combustion engine which is formed with at least one working space (130, 132) delimited by a piston (22) with fuel injection, characterized in that an injection device (150) is arranged in a separate combustion chamber (152) which is adjacent to the working space ( 130) connects, the combustion chamber (152) and fuel injection being coordinated so that the combustion essentially takes place only in the combustion chamber (152), so that only burned, expanding exhaust gas enters the working space (130, 132).