EP1597456B1 - Rotary piston machine with an oval rotary piston guided in an oval chamber - Google Patents

Description

• (a) die Ordnung des Ovals der Kammer um eins geringer ist als die Ordnung des Ovals des Rotationskolbens,
• (b) der Durchbruch dem Rotationskolben im wesentlichen mathematisch ähnlich ist, wobei die Symmetrieebenen des Durchbruchs mit denen des Rotationskolbens zusammenfallen, und
• (c) ein Paar mit Außenverzahnung versehene, gehäusefest gelagerte Wellen vorgesehen sind, deren Außenverzahnungen mit der Innenverzahnung des Durchbruchs in Eingriff sind, wobei in jedem Bewegungsabschnitt des Rotationskolbens jeweils ein Bereich eines Abschnitts der Innenverzahnung des Durchbruchs mit kleinerem Krümmungsradius mit der Außenverzahnung einer der Wellen in Eingriff ist, während ein Abschnitt der Innenverzahnung des Durchbruchs mit größerem Krümmungsradius mit der Außenverzahnung der anderen Welle in Eingriff ist und im jeweils folgenden Bewegungsabschnitt jeweils ein Bereich eines Abschnitts der Innenverzahnung mit größerem Krümmungsradius mit der Außenverzahnung der ersteren Welle in Eingriff ist, die im vorangegangenen Bewegungsabschnitt mit einen Bereich eines Abschnitts von kleinerem Krümmungsradius in Eingriff war, während die Außenverzahnung der Welle, die im vorangegangenen Bewegungsabschnitt mit einen Bereich eines Abschnitts der Innenverzahnung des Durchbruchs von größerem Krümmungsradius in Eingriff war, nun mit einem Bereich eines Abschnitts von kleinerem Krümmungsradius in Eingriff ist.

The invention relates to a rotary piston machine, comprising a prismatic chamber formed in a housing, whose cross section forms an oval of circular arcs of alternately smaller and larger radius, and a rotary piston movable in the chamber, whose cross section is also an oval with the same alternately smaller and larger radii whose order deviates from the order of the oval forming the cross-section of the chamber, the rotary piston alternately rotating in successive stages of movement about different axes of rotation from one stop position to the next, and rotating in any position on the inner wall of the chamber to form two Working chambers abuts, and provided with an internal toothing breakthrough of the rotary piston, the internal toothing with an external toothing of at least one housing fixedly mounted shaft for the drive or the output of the rotary motion is engaged, in which

• (a) the order of the oval of the chamber is one less than the order of the oval of the rotary piston,
• (b) the aperture is substantially mathematically similar to the rotary piston, the planes of symmetry of the aperture coinciding with those of the rotary piston, and
• (C) a pair of externally toothed, housing fixedly mounted shafts are provided, the outer teeth are in engagement with the internal teeth of the aperture, wherein in each movement portion of the rotary piston, in each case a portion of a portion of the inner teeth of the smaller radius of curvature of the outer toothing of the waves is engaged, while a portion of the internal teeth of the opening with a larger radius of curvature with the outer teeth of the other shaft is engaged and in the following each movement section, a portion of a portion of the inner toothing with a larger radius of curvature with the outer toothing of the former shaft is engaged in the the previous movement portion with a portion of a portion of smaller radius of curvature was engaged, while the outer teeth of the shaft, in the previous movement portion with a portion of a portion of the internal teeth of the larger radius of curvature breakthrough is now engaged with a portion of a smaller radius of curvature portion.

An "oval" in mathematics is a non-analytic, closed, flat convex figure composed of circular arcs. The circular arcs are continuous and differentiated juxtaposed. In the points where the circular arcs connect, the curve is continuous. There are also the tangents of the two adjoining circular arcs together. The curve is differentiable. In the points where the circular arcs with different radii of curvature join, 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 having the first and second radii of curvature. A second-order or bi-oval oval is "ellipse-like" with two diametrically opposed circular arcs of smaller diameter joined by two circular arcs of larger diameter.

State of the art

Rotary piston machines of the type mentioned are known.

The US 3,967,594 A and the US 3 996 901 A show a rotary piston machine with an oval piston in an oval chamber. The piston is bi-oval in cross-section. This bi-oval piston is movable in a tri-oval chamber. In these known rotary piston machines complex gears are provided to transmit the rotational movement of the rotary piston on a shaft.

The DE 199 20 289 C1 also describes a rotary-piston machine in which the cross-section of a prismatic chamber formed in a housing is tri-oval with first and second arcs of alternately a smaller radius of curvature and a larger radius of curvature contiguous and differentiable. In the chamber, a rotary piston is guided with bi-oval cross-section. The bi-oval cross-section of the rotary piston is formed by alternately first and second circular arcs with the smaller or larger radii of curvature of the tri-oval cross-section of the chamber, which again connect continuously and differentially to each other. The bi-oval rotary piston performs in the tri-oval chamber the motion cycles described above with jumping momentary axes of rotation. The movement of the rotary piston is tapped there in a very simple manner: A shaft extends centrally through the tri-oval chamber, ie along the line of intersection of the symmetry planes of the chamber. The shaft carries a pinion. The rotary piston has an oval opening with an internal toothing. The long axis in cross section of the aperture extends along the short axis of the bi-oval cross-section of the rotary piston. The pinion meshes constantly with the internal teeth.

In the known rotary piston machines, a housing forms a prismatic chamber whose cross-section such an oval odd order, so for example a Oval forms third order. The chamber forms cylindrical inner wall sections alternately with the first, small and the second, larger radius of curvature. In such an oval of third (fifth or seventh and higher) order is a rotary piston movable, which forms an oval in cross-section, whose order is one less than the order of the oval of the chamber. The oval used for the rotary piston has a two-fold 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 opposite cylindrical shell sections whose radius of curvature corresponds to the smaller (first) radius of curvature of the oval of the chamber. When 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 of the rotary piston is located with a first of these cylindrical shell portions in a complementary cylindrical inner wall portion of the chamber, which has the same smaller radius of curvature. With the second, diametrically opposed cylindrical shell portion of the rotary piston slides on the opposite cylindrical inner wall portion of the chamber, which has the larger radius of curvature. In the chamber, two working spaces are formed in this way by the Rotatioskolben, of which one increases during rotation of the rotary piston and the other is smaller. The rotary piston rotates about a momentary axis of rotation. This instantaneous axis of rotation coincides with the cylinder axis of the first cylindrical shell portion. This instantaneous axis of rotation therefore has a defined position relative to the rotary piston. The instantaneous axis of rotation in this movement section of course also corresponds to the housing-fixed cylinder axis of the cylindrical inner wall section of smaller radius of curvature, in which the rotary piston rotates. This rotation continues until the second cylindrical skirt portion of the rotary piston enters a stop position. In this stop position, the second cylindrical shell portion lies in the adjoining the opposite inner wall portion of larger radius of curvature inner wall portion of smaller diameter.

A further rotation of the rotary piston to the previous current pivot point is not possible. The current axis of rotation therefore jumps for the next Movement section in a different position, namely the cylinder axis of the second cylindrical shell portion. This new instantaneous axis of rotation is in a defined position relative to the rotary piston. It corresponds in the next movement portion of the cylinder axis of the cylindrical inner wall portion in which now rotates the second cylindrical shell portion of the rotary piston. The "first" cylindrical shell portion slides in this movement section again on the opposite inner wall portion 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 about different instantaneous axes of rotation, wherein the axes of rotation "jump" after each movement section. Based on the rotary piston two such instantaneous axes of rotation are defined, namely by the cylinder axes of the diametrically opposed cylindrical shell sections. Based on the housing and the chamber formed therein, the instantaneous 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.

In each movement section, the volume of a working space grows up to a maximum value, while the volume of the other working space decreases to a minimum value. Ideally, if the rotary piston also forms an oval in cross section, the volume of the working space increases from practically zero to the maximum value or decreases to virtually zero. Such a rotary piston engine may be used as a two-stroke or four-stroke internal combustion engine or as an external combustion engine, e.g. Steam engine, be trained. But it can also work as an air pressure motor, as a hydraulic motor or as a pump.

In the DE 199 20 289 C1 is in a chamber whose cross-section forms a third-order oval, a rotary piston movable, whose cross-section is a second-order oval. To pick up the movement of the rotary piston is a single centrally extending through the chamber output shaft. The output shaft protrudes through an oval opening of the rotary piston and carries a pinion. The pinion is in mesh with a toothing on the inside of the aperture.

In the known rotary piston engines, the order of the oval defining the chamber is one greater than the order of the oval forming the cross section of the rotary piston. A bi-oval rotary flask is guided in a tri-oval chamber. In this case, jump the instantaneous 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 translates with the small radius portion on the large radius portion of the inner wall of the chamber. This can lead to sealing problems in the sealing between the working chambers of the chamber. Another problem arises from the fact that in each cycle of the rotary piston machine successively more than two working spaces are formed, which wander along the inner wall of the housing.

Luxembourg patent application LU 45663 discloses a rotary piston machine having a rotary piston in the form of a third order oval (three rounded "corners") in a second order oval shaped chamber (two rounded "corners"). In the rotary piston, a recess with a continuous, uniform toothing is provided in one of the flat surfaces. The recess has a shape corresponding to the oval of the rotary piston. In the toothing of the recess engage external teeth of two fixed housing fixed waves. The one shaft serves to transmit the drive force, while the other shaft is provided for regulating the piston movement and for driving an alternator and a radiator fan.

Disclosure of the invention

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

The invention is further based on the object to ensure a closed kinematics with clear movement of the rotary piston in a simple manner in the stop positions of the rotary body.

The invention is for this purpose specifically the task to reduce the number of occurring relative to the housing current axes of rotation.

The invention is finally based on the object, a rotary piston machine of the type mentioned in such a way that only two alternately increasing and decreasing work spaces occur, which are arranged opposite in fixed angular positions to the housing.

According to the invention, these objects are achieved in that provided in a rotary piston machine of the type mentioned sensors for signaling the achievement of a stop position by the rotary piston and speed control means with an acted upon by the signals of the sensors control and each controlled by the controller braking device for each of the waves are with which upon reaching a stop position in each case that shaft whose outer toothing unrolled in the previous movement section on the internal teeth of the opening in the region of a larger radius of curvature is temporarily braked, while the other shaft rotated about the axis of the rotary piston in the previous movement section remains unchecked ,

Surprisingly, one obtains a clear guidance of a cross-sectionally oval rotary piston in an oval chamber to form mutually sealed working spaces even if the rotary piston, in contrast to the prior art, has a higher order of the oval than the chamber, e.g. a triovaler rotary piston rotates in a bi-oval chamber. The rotation takes place in each case about one of two instantaneous axes of rotation, which are formed here but of housing-fixed shafts. The axes of rotation have gears or external gears. which are in engagement with an internal toothing of a substantially oval opening of the rotary piston. One of the shafts in each case sits in a region of the smaller radius of curvature of the oval opening, thus e.g. virtually in a "corner" of the breakthrough forming "arch triangle". The other shaft is in engagement with the opposite region of the internal toothing with the larger radius of curvature, so to speak, the opposite side of the arch triangle.

In a stop position is located in a rotary piston machine with bi-oval chamber and tri-oval rotary piston of the rotary piston with two adjacent regions with a larger radius of curvature and the intermediate region of smaller radius of curvature at the inner wall of the chamber. When the rotary piston enters such a stop position, the other shaft is also located in a corner of the arch triangle. The further rotation of the rotary piston takes place in the same direction of rotation then around the first-mentioned wave. Again, therefore, the axes of rotation jump when reaching a stop position. But this jumping takes place between two fixed axes, namely between the axes of rotation of the two shafts.

In general, in a 2n-oval chamber, the rotary piston guided therein has the order 2n + 1. In the stop positions then the rotary piston with n + 1 "sides" is positively against the inner wall of the chamber, while each n "sides" limit that working chamber, which then has its maximum extent. Two work spaces are formed on opposite sides of the housing.

In the stop positions, the kinematics of the rotary piston is not completed in the chamber. Instead of another rotary motion, e.g. occur by the introduction of a pressure medium in the minimized working volume or by igniting a fuel mixture, a transverse force, which leads to jamming of the rotary piston in the chamber. In order to solve this problem and to obtain a completed kinematics, according to the invention speed-regulating means are provided with which when reaching a stop position for that shaft whose outer teeth rolled in the previous movement section with the internal teeth of the opening in the region of a larger radius of curvature, a lower speed can be forced than for the other shaft about the axis of the rotary piston rotated in the previous movement section. This ensures that the rotary piston continues to rotate in the intended manner around the shaft which is forced to rotate at a lower speed. This forced speed specification only needs to be made for a short time until the rotary piston has unscrewed from the stop position. The forced speed specification can take place in that one of two housing-fixed shafts is braked by braking means, which is structurally easy to accomplish.

On one side, a peripheral portion of the rotary piston rotates relatively slowly on a circumferential portion with a large 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 large-radius-of-rotation rotary piston slides on just such a peripheral portion of the inner wall. This results in a large sealing surface.

Fig.1

zeigt einen Querschnitt einer Rotationskolbenmaschine mit zwei Wellen, wobei ein Rotationskolben, dessen Querschnitt ein Oval dritter Ordnung bildet, in einer Kammer geführt ist, deren Querschnitt ein Oval zweiter Ordnung ist.

Fig.2

ist eine Darstellung ähnlich Fig.2 und zeigt den Rotationskolben in einer Anschlagstellung.

Fig.3

ist eine Darstellung ähnlich Fig.2 und zeigt den Rotationskolben während des nächsten Bewegungsabschnitts.

Fig.4

zeigt einen Querschnitt einer Rotationskolbenmaschine mit zwei Wellen, wobei ein Rotationskolben, dessen Querschnitt ein Oval fünfter Ordnung bildet, in einer Kammer geführt ist, deren Querschnitt ein Oval vierter Ordnung ist.

Fig.4A

zeigt eine Abwandlung der Anordnung nach Fig.4.

Fig.5

zeigt einen Querschnitt einer Rotationskolbenmaschine mit zwei Wellen, wobei ein Rotationskolben, dessen Querschnitt ein Oval siebter Ordnung bildet, in einer Kammer geführt ist, deren Querschnitt ein Oval sechster Ordnung ist.

Fig.6

ist eine schematische Darstellung der drehzahlregulierenden Mittel.

Fig.7A

ist eine schematische, vergrößerte Darstellung der Dichtung bei einer Rotationskolbenmaschine der in den Figuren 1 bis 5 dargestellten Art, wobei die Abdichtung zwischen einer Dichtleiste und einem Umfangsabschnitt des Rotationskolbens mit kleinerem Krümmungsradius erfolgt.

Fig.7B

ist eine schematische, vergrößerte Darstellung der Dichtung bei einer Rotationskolbenmaschine der in den Figuren 1 bis 5 dargestellten Art, wobei die Abdichtung zwischen einer Dichtleiste und einem Umfangsabschnitt des Rotationskolbens mit größerem Krümmungsradius erfolgt.

Fig.8

zeigt in vergrößertem Maßstab eine Einzelheit der Rotationskolbenmaschine von Fig.4A.

Fig.8A

zeigt die Einzelheit von Fig.8 in weiter vergrößertem Maßstab.

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

Fig.1

shows a cross section of a rotary piston machine with two shafts, wherein a rotary piston whose cross section forms a third-order oval, is guided in a chamber whose cross section is a second-order oval.

Fig.2

is a representation similar Fig.2 and shows the rotary piston in a stop position.

Figure 3

is a representation similar Fig.2 and shows the rotary piston during the next movement section.

Figure 4

shows a cross section of a rotary piston machine with two shafts, wherein a rotary piston whose cross section forms a fifth-order oval, is guided in a chamber whose cross-section is a fourth-order oval.

4A

shows a modification of the arrangement according to Figure 4 ,

Figure 5

shows a cross section of a rotary piston machine with two shafts, wherein a rotary piston whose cross section forms a seventh-order oval, is guided in a chamber whose cross section is a sixth order oval.

Figure 6

is a schematic representation of the speed-regulating means.

7A

is a schematic, enlarged view of the seal in a rotary piston machine in the FIGS. 1 to 5 illustrated type, wherein the seal between a sealing strip and a Peripheral portion of the rotary piston with a smaller radius of curvature takes place.

7B

is a schematic, enlarged view of the seal in a rotary piston machine in the FIGS. 1 to 5 illustrated type, wherein the seal between a sealing strip and a peripheral portion of the rotary piston takes place with a larger radius of curvature.

Figure 8

shows in enlarged scale a detail of the rotary piston machine of 4A ,

8A

shows the detail of Figure 8 in a further enlarged scale.

In Fig.1 is designated 10 a housing. In the housing 10, a chamber 12 is formed. The cross section of the chamber 12 forms a second order oval or is "bi-oval". The cross-section of the chamber 12 is thus formed by two circular arcs 14 and 16 of relatively small radius of curvature and alternately between two circular arcs 18 and 20 of relatively large radius of curvature. The circular arcs close to each other steadily and differentially.

In the chamber 12, a rotary piston 22 is guided. The cross-section of the rotary piston 22 forms a third-order oval or is tri-oval. Accordingly, the circumference of the cross-section of three pairs of a circular arc of relatively small radius of curvature 24, 26 and 28 and a circular arc of relatively large radius of curvature 30, 32 and 34 is formed. The circular arcs of small and large radius of curvature close to each other alternately and also steadily and differentially. The small radii of curvature of the rotary piston 22 are equal to the small radii of curvature of the chamber 12, and also the large radii of curvature of the rotary piston 22 are equal to the large radii of curvature of the chamber 12. The cross section of the chamber 12 is similar to an ellipse, even though it is not an ellipse. The cross section of the rotary piston 22 is similar to an arch triangle with rounded corners.

The rotary piston 22 has a central opening 36. The cross section of the aperture 36 also forms a third order oval. This third order oval is formed by three circular arcs of relatively small radius of curvature 38, 40 and 42 and by three circular arcs 44, 46 and 48 of relatively large radius of curvature. The circular arcs 38, 40 and 42 with a small radius of curvature and the circular arcs 44, 46 and 48 of large radius of curvature are adjacent to each other alternately and steadily and differentially, so that an oval is formed similar to an arch triangle with rounded ends. The planes of symmetry 50, 52 and 54 of the aperture 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-arc toothed racks 58, 60 and 62 substantially along the circular arcs 44, 46 and 48 of large radius of curvature. Between these concave-arcuate toothed racks 58, 60 and 62, convex arcuate (or optionally straight) toothed racks 64, 66 and 68 are provided in the region of the circular arcs of small radius of curvature.

Through the aperture 36, two parallel shafts 70 and 72 extend with gears 74 and 76, respectively. The axes of the shafts 70 and 72 lie in the plane of symmetry 77 of the chamber 12 through the circular arcs 18 and 20. The gear of one shaft, in Fig.1 the gear 74 of the shaft 70, sitting in the "corner of the arch triangle", ie in the region of the circular arc 38 of small radius of curvature and is with the internal teeth 56 in a manner to be described in engagement. The gear of the other shaft, in Fig.1 the gear 76 of the shaft 72 is, with the opposite concave-arc-shaped rack, in Fig.1 the rack 60, in engagement.

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 with internal combustion. Accordingly, for each working space 80 and 82, an inlet valve 84 and 86 and an outlet valve 88 and 90, respectively. Furthermore, closes at each working space 80 and 82 a Combustion chamber 92 and 94 with a spark plug or an injector 96 or 98 at. The work spaces 80 and 82 with the valves and spark plugs or injectors are symmetrical to the plane of symmetry passing through the circular arcs 14 and 14 of the small radius of curvature cross section. That's just a schematic illustration.

In regions 18 and 20 of the large radii of curvature, pairs of adjoining sealing strips 100A, and 100B, 102A, and 102B are provided on the housing. The sealing strips 100A and 100B or 102A and 102B are symmetrical to the plane of symmetry passing through the circular arcs 18 and 20 of the cross section with a large radius of curvature.

7A shows the sealing strips 100A and 100B at a position in the region of the transition from the smaller radius of curvature r _{1 of} the outer surface of the rotary piston 22 right in 7A to the area of the larger radius of curvature r _{2 of} this outer surface left in 7A , The sealing strip 100A has a concave-cylindrical inner surface whose radius of curvature 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 ₁ . It can be seen that the inner surface of the sealing strip 100A in the region of the radius of curvature r _{2 of} the rotary piston 22 rests tightly against the surface of the rotary piston 22 complementary thereto. In the region in which the radius of curvature of the surface of the rotary piston 22 is smaller, namely r ₁ , 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 radius of curvature r ₁ . It can be seen that the inner surface of the sealing strip 100B in the region of Krfunmungsradius r _{1 of} the rotary piston 22 tightly against the complementary surface of the rotary piston 22 applies. In the region in which the radius of curvature of the surface of the rotary piston 22 is greater, namely again r ₂ , is formed on the right in 7A between the sealing strip 100B and the rotary piston 22 and the inner surface of the sealing strip 100A a wedge-shaped gap 100D. In the illustrated transition region both sealing strips are each on one Part of the inner surface in planar contact with the outer surface of the rotary piston, so that a surface seal is ensured.

7B Similarly, the seal in the region of the transition from the large radius of curvature r ₂ to the smaller radius of curvature r ₁ . If the pair of sealing strips 100A and 10B abuts only a portion of the rotary piston 22 having a large radius of curvature r ₂ or only a portion of a small radius of curvature, either the sealing strip 100A or the sealing strip 100B ensures surface contact and sealing with the entire inner surface, respectively.

• Der Rotationskolben 22 dreht sich entgegen dem Uhrzeigersinn in Fig.1. Dabei dreht sich der Rotationskolben 22 um die Welle 70 und gleitet mit geringer Geschwindigkeit an der Innenwand der Kammer 12 im Bereich des großen Krümmungsradius. Die Achse der Welle 70 geht durch den Krümmungsmittelpunkt des Kreisbogens 24 von kleinem Krümmungsradius. Der Kreisbogen 24 tangiert den Kreisbogen 18 des Querschnitts der Kammer 12. Der gegenüberliegende, dem Kreisbogen 32 entsprechende Bereich der Mantelfläche des Rotationskolbens 22 mit dem großen Krümmungsradius liegt an dem dem Kreisbogen 20 entsprechenden Bereich der Innenwandung der Kammer 12 an. Dieser Bereich der Innenwandung hat den gleichen Krümmungsradius wie der anliegende Bereich der Mantelfläche des Rotationskolbens. Es erfolgt also eine formangepaßte, flächige Anlage. Bei der Drehbewegung gleitet dieser Bereich der Mantelfläche des Rotationskolbens an dem entsprechenden Bereich der Innenwandung.

The described arrangement works as follows:

• The rotary piston 22 rotates counterclockwise in FIG Fig.1 , In this case, the rotary piston 22 rotates about the shaft 70 and slides at low speed on the inner wall of the chamber 12 in the region of the large radius of curvature. The axis of the shaft 70 passes through the center of curvature of the circular arc 24 of small radius of curvature. The circular arc 24 is tangent to the circular arc 18 of the cross section of the chamber 12. The opposite, the circular arc 32 corresponding region of the lateral surface of the rotary piston 22 with the large radius of curvature is located on the circular arc 20 corresponding portion of the inner wall of the chamber 12. This region of the inner wall has the same radius of curvature as the adjacent region of the lateral surface of the rotary piston. So there is a form-adapted, areal plant. During the rotational movement of this region of the lateral surface of the rotary piston slides on the corresponding region of the inner wall.

In this case, the working space 80 increases while the working space 82 decreases. The shaft 70 is thereby rotated relatively slowly, while a relatively fast rotation of the shaft 72 results.

This movement will continue until the in Fig.2 right stop position is reached. Then, the area corresponding to the circular arc 28 of the lateral surface of the rotary piston in the region 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 circular arcs 32 and 34 with the large radius of curvature corresponding areas of the lateral surface of the rotary piston are applied to the areas 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 combustion chamber 94, while the work chamber 82 has its maximum volume. The shaft 72 with the gear 76 is then in the opening 36 in the area corresponding to the arc 40, so to speak in the lower left "corner" of the arch triangle. The rotary piston 22 can not now rotate about the axis of the shaft 70 as a current axis of rotation.

This position is in Fig.2 shown.

In a further rotation, e.g. is caused by igniting fuel in the combustion chamber 94 in an internal combustion engine or by introducing a working medium in the working chamber 82, the instantaneous axis of rotation jumps in the axis of the shaft 72. The rotary piston continues to rotate counterclockwise, but now about the shaft 72nd

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

During the rotary movement of the rotary piston 22, successive movement sections occur. Each movement section extends from one of the described stop positions to the next. In each movement section, a workspace, eg 80, increases from zero to a maximum, while the other workspace decreases from the maximum to zero. In the next movement section, it is the other way round: the working space 82 increases from zero ( Fig.2 ) to a maximum while the working space 80 decreases again ( Figure 3 ).

In the position of Fig.2 the kinematics is not unique. Each of the two waves could define an instantaneous axis of rotation with its axis. For example, if a force is applied to the left on the rotary piston 22 by a working medium introduced into the working space 82, this force could possibly cause a rotation of the rotary piston 22 about a momentary axis of rotation to a translatory movement in the horizontal direction Fig.2 to lead. As a result, the rotary piston 22 would be wedged in the chamber 12.

If this danger exists, it can be countered by being in the position of Fig.2 By speed-regulating means a lower speed of the shaft 72 is forced for a short time than the rotational speed of the shaft 70. Then, the rotary piston 22 is forced to rotate about this shaft 72, while the other shaft 70, a rolling of the concave-arc toothed rack 62 on the gear 74 allowed.

Is in Figure 6 shown schematically. Sensors 140 detect the position of the rotary piston at 22 in chamber 12. The sensors signal when the rotary piston has reached a stop position. A controller 142 acted upon by the signals from the sensors then controls devices 144 and 146, by means of which rotational speeds of the shaft 70 or the shaft 72 are preset for a short time, depending on which stop position has been reached. He is then given eg the shaft 70 a low speed and the shaft 72 a higher or vice versa. In the simplest case, the devices 144 and 146 may be braking devices which, in the stop positions, act alternately on the shaft 70 or the shaft 72 for a short time while the respective other shaft remains unbraked.

The radii of the pitch circles of the gears correspond substantially to the small radii of curvature of the opening 36 forming the second order oval. If the internal teeth 56 were to follow the oval of the aperture 36 throughout, then the gears would each be caught in the end positions of the rotary piston 22. The "corners" of the "Arch Triangle" could not roll over the gears. For this reason, the concave arcuate toothed racks in the region of circular arcs 38, 40, 42 are connected with a small diameter by short straight or convex-arcuate toothed racks 64, 66 and 68, respectively. The convex-arcuate toothed racks 64, 66 and 68 allow further rotation of the internal teeth 56 and thus of the rotary piston 22 over these areas. They are dimensioned so that in the stop positions each one of the concave-arched toothed racks 58, 60 or 62 with the gear 74 or 76 engages immediately after the engagement of the gear 74 or 76 with the previous rack 62, 58 and 60 solved has been. In this way, each gear is constantly engaged with one of the concave arcuate racks 64, 66 or 68. The short convex-arcuate or straight racks ensure a transition without interruption of the positive connection but also without blocking.

Figure 4 shows a rotary piston machine with a chamber 104, whose cross section forms a fourth order oval 106 In the chamber 104, a Rötationskolben 108 is stirred, the cross section of a fifth order oval 110 forms. Again, the rotary piston 108 has an opening 112 whose shape forms a fifth-order oval 114. The symmetry axes of rotary piston 108 and aperture 112 coincide. The aperture 112 has internal teeth 116. The internal teeth 116 engage with two gears 118 and 120. The gears 118 and 120 are seated on two shafts 122 and 124 fixed to the housing. The shafts 126 and 128 of the shafts 122 and 124, respectively, lie in a plane of symmetry of the chamber 104.

The rotary piston 108 divides the chamber into two working chambers 130 and 132, one of which increases in rotation of the rotary piston and the other decreases.

The workflow is similar to the workflow of running Fig.1 to 3 , The rotary piston 108 rotates, for example, about the axis 126 of a shaft 122 to a stop position. Then the instantaneous axis of rotation jumps into the axis 128 of the other shaft 124. The rotary piston rotates about this axis further counterclockwise from Figure 4 until 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 work spaces are always on both sides of the axes 126 and 128 the waves 122 and 124 containing symmetry plane. They do not wander around the chamber.

In Figure 4 For each workspace (schematic) valves and spark plugs or injectors are shown.

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

In the rotary piston machine of 4A is designated with 150 an injection nozzle. The injection nozzle 150 protrudes into a combustion chamber 152. This combustion chamber is dimensioned and designed so that the combustion of the injected fuel takes place substantially only in the combustion chamber. In the expanding workspace then only the expanding combustion gases enter. In this case, the injection can be metered depending on the time or in dependence on the rotation of the rotary piston so that it is adapted to the change in volume of the working space 130 or 132. In the working space then no flame front occurs. The propagation of flame fronts in an expanding workspace presents problems with known rotary piston engines.

In the execution of Figure 8 and 8A The combustion chamber 152 has a spherical-cap-shaped recess of the housing, to which a frustoconical space 156, which tapers towards the working space, adjoins. The space 156 is formed in an insert 158, which is screwed into a threaded recess of the wall of the working space 130 or 132. The combustor 152 is closed by a grid or net 160. The injection nozzle 150 empties 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 substantially only in the combustion chamber and flame fronts in The workrooms are avoided, is also applicable to other machines, such as reciprocating engines.

Figure 5 shows a rotary piston machine in which a rotary piston whose cross section forms a seventh-order oval, is guided in a chamber whose cross section is a sixth order oval. Structure and function are similar to the execution of ovals, except for the orders of the ovals Figure 4 , Corresponding parts are provided with the same reference numerals as in FIG Figure 4 but with the addition "A".

Claims (4)

1. Rotary piston machine having a prismatic chamber (12) in a housing (10), the cross section of the chamber being an oval formed by circular arcs (14, 16; 18, 20) with alternating smaller and larger radius, and a rotary piston (22) movable in the chamber (12), the cross section of the rotary piston being also an oval with the same alternating smaller and larger radii and an order different from the order of the oval defining the cross section of the chamber (22), wherein the rotary piston (22) alternately rotates, in successive intervals of motion, around different axes of rotation from one blocking position to the next one respectively and, during the rotational movement, in any position engages the inner wall of the chamber (12) forming two working chambers (80, 82), and having an aperture (36) of the rotary piston (22) provided with an internal toothing (56), the internal toothing (56) engaging an external toothing (74, 76) of at least one housing-fixed mounted shaft (70, 72) for driving the rotary motion or for being driven thereby, wherein

   (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 substantially mathematically similar to the rotary piston (22), wherein the planes of symmetry (50, 52, 54) of the aperture (36) coincide with those of the rotary piston (22), and

   (c) a pair of shafts (70, 72) provided with external toothing (74,76) and mounted housing-fixed is provided, the external toothing (74, 76) engaging the internal toothing (56) of the aperture (36), wherein in any interval of motion of the rotary piston (22) one area of a section (38) of the internal toothing (56) of the aperture (36) with smaller radius of curvature (r₁) engages the external toothing (74, 76) of one of the shafts (70, 72) respectively, while a section (46) of the internal toothing (56) of the aperture (36) with larger radius of curvature (r₂) engages the external toothing (74, 76) of the other shaft (70, 72), and in the respective following interval of motion an area of a section (44) of the internal toothing (56) with larger radius of curvature (r₂) engages the external toothing (74, 76) of the former shaft (70,72), which was in engagement with an area of a section having a smaller radius of curvature (r₁) in the preceding interval of motion, while the external toothing (74, 76) of the shaft (70,72), which was engaging an area of a section (46) of the internal toothing (56) of the aperture (36) with larger radius of curvature (r₂) in the preceding interval of motion, now is engaging with an area of a section (42) having a smaller radius of curvature (r₁),

   characterised in that

   (d) sensors (140) for signalling the reaching of a blocking position by the rotary piston, and rotary speed regulating means (142,144,146) having a control (142) to which the signals of the sensors are applied, and a brake device (144, 146) controlled by the control (142) for each of the shafts (70, 72) respectively are provided, by means of which, when a blocking position has been reached, the respective shaft (70 or 72), which external toothing (74 or 76) unrolled on the internal toothing (56) of the aperture (36) in an area with larger radius of curvature in the previous interval of motion, is temporarily braked, while the other shaft (72 or 70), around the axis of which the rotary piston (22) rotated in the previous interval of motion, remains unbraked.
2. Rotary piston machine according to claim 1, characterised in that pairs of adjacent arranged sealing ledges (100A, 100B) having concave-cylindrical inner surfaces are provided in the inner wall of the chamber (12) for sealing between the working chambers, wherein the radius of the curvature of one inner surface is equal to the smaller radius of curvature (r₁) and the radius of curvature of the other inner surface is equal to the larger radius of curvature (r₂) of the lateral surface of the rotary piston (22).
3. Rotary piston machine according to claim 2 characterised in that, two pairs of sealing ledges (100A, 100B) are arranged opposite to one another.
4. Rotary piston machine according to one of claims 1 to 3 wherein the rotary piston machine is designed as internal combustion engine with internal combustion in at least one working chamber (130, 132) limited by the rotary piston (22) and with fuel injection, characterised in that an injection device (150) is arranged in a separate combustion chamber (152) which is connected with the working chamber (130, 132), the combustion chamber (152) and fuel injection being adapted such that combustion takes place substantially in the combustion chamber (152) only, whereby only combusted, expanding exhaust gas enters the working chamber (130, 132).

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