WO2012130925A2

WO2012130925A2 - Rotary piston engine

Info

Publication number: WO2012130925A2
Application number: PCT/EP2012/055606
Authority: WO
Inventors: Boris Schapiro
Original assignee: Boris Schapiro
Priority date: 2011-04-01
Filing date: 2012-03-29
Publication date: 2012-10-04
Also published as: WO2012130925A3; DE102011001752A1

Abstract

The invention relates to a rotary piston engine (10), which comprises a housing (12) having an inner, epitrochoid-shaped shell surface (14) and a rotary piston (18) having two arcuate piston shell surfaces (20, 22) and two corners (24, 26). The rotary piston (18) rotates in the interior (16) about the center point (28) of the rotary piston while the center point (28) travels a circular path (32). Both arcuate piston shell surfaces (20, 22) are designed in such a way that each lies against a first shell section (36) of the shell surface (14) in a form-closed manner at a specific respective rotational position. Furthermore, a separate combustion chamber (54) is arranged in the housing (12), having a passage (56) to the interior (16) in the area of the first shell section (36) of the shell surface (14). The invention further relates to a rotary piston engine (100) comprising at least two rotary pistons (102, 104) and a central combustion chamber (112), wherein all interiors (106, 108) and rotary pistons (102, 104) are arranged in point symmetry with respect to the center point (124) of the combustion chamber (112). Furthermore, the invention relates to sealing assemblies (210, 250) for rotary piston machines.

Description

Rotary piston internal combustion engine

Technical area

The invention relates to a rotary piston internal combustion engine, comprising a) a housing having an inner, epitrochoidal lateral surface along a single closed Trochoidbogen, the lateral surface together with two side surfaces forms an interior of the housing, b) a rotary piston with two arcuate Kolbenmantelfiächen, which symmetrical to C) rotates the rotary piston in the interior and thereby rotates about its center, while the center passes through a circular path, both corners during rotation constantly at the epitrochoidal Abut surface and both arcuate Kolbenmantelfiächen are formed so that each rests positively in each case in a certain rotational position on a first jacket portion of the lateral surface. Furthermore, the invention relates to a rotary piston internal combustion engine, which contains at least two rotary pistons and a housing, each having an inner space for each rotary piston, in which rotate the rotary piston. Furthermore, the invention relates to sealing arrangements for a rotary piston of a rotary piston machine for sealing the rotary piston against a trochoidförmigen Innenmantelfiäche a housing during rotation of the rotary piston, which has a seal in a groove which is parallel to the axis of rotation of the rotary piston.

State of the art

There are a variety of rotary piston machines are known in which a rotary piston rotates in a rotation about its center of gravity and at the same time the center of gravity of the rotary piston rotates on a circular path. These rotary piston machines are referred to as rotary piston engines. An example of a rotary engine is the well-known Wankel engine. The combination of two circular movements causes the lateral surface of the piston chamber, in which the rotary piston rotates, to run along a trochoid.

As a trochoid, the trajectory of a point attached to a circle when rolling the circle is called. The point may also be outside or inside the circle. If the circle rolls off at a second circle, the trajectory is called epitrochoid. An epitrochoid, in which the first circle rolls around an inner second circle, is also called peritrochoide. The shape of these epitrochoidals is particularly dependent on the ratio of the circle radii and the distance of the point from the center of the first circle. Furthermore, the shape of the epitrochoid of the lateral surface of a rotary piston machine specifies the exact piston shape. This results as the inner envelope of the pattern, which arises when rolling the inner second circle with a point attached to the epitrochoid at the outer circle. More about this and mathematical Descriptions can be found, for example, in W.-D. Bensinger, "Rotary Piston Internal Combustion Engines", Springer-Verlag, Berlin, Heidelberg, New York, 1973 and Kenichi Yamamoto, "Rotary Engine", Sankaido Co. Ltd., Tokyo, 1981. In the Wankel engine, the ratio of the circle radii is 2: 3. This relationship is directly reflected in geometry. The epitrochoid of the piston chamber has two Trochoidbögen and the rotary piston has three corners or arcuate lateral surfaces. Rotary engines with other ratios of the radii of the circle are also known. Thus, for example, by Felix Wankel, "Division of rotary piston engines", Deutsche Verlags- Anstalt, Stuttgart, 1963 or in US Patent US 5,317,996 A also a 1: 2 geometry with a lateral surface of the piston chamber along a single closed Trochoidbögen and a Rotary piston with two corners or two arcuate Kolbenmantelfiächen described.

The compression of air or a fuel mixture takes place in the known rotary piston internal combustion engines in the piston chamber by the rotating rotary piston. In addition, combustion troughs may be provided in the piston skirt surfaces. The disadvantage here is that the compression ratio of the geometry of the rotary piston machine depends and this can vary only within narrow limits. For example, it causes problems to achieve the necessary compression ratios for a diesel engine in a rotary engine. The efficiency of a rotary piston engine depends directly on the compression ratio. The sealing of the rotary piston with respect to the trochoidal lateral surfaces of the piston chamber plays a decisive role for the compression ratio. In contrast to a reciprocating engine with a surface-to-surface seal between the reciprocating piston and the cylindrical side wall, the sealing of the rotary piston with its corner on the trochoidal lateral surface is a line-to-surface seal. The curvature of the lateral surface is different along the trochoid , In addition, during rotation, the angle between the axis of symmetry of the rotary piston changes through the corner and the normal the lateral surface. The sealing of the rotary piston relative to the lateral surface of the piston chamber is still an unsatisfactorily solved problem.

In rotary piston engines rotate all the essential, moving parts, in particular rotary piston and eccentric shafts. This circumstance leads to a much less vibratory compared to reciprocating and softer run. However, since, for example, in rotary engines, the center of gravity of the rotary piston in turn passes through a circle, they must be fully balanced. This measure leads disadvantageously to an increase in weight and space requirements in rotary piston engines. Remaining vibrations can affect the seal between the rotary piston and the lateral surface and thus also adversely affect the compression ratio.

Disclosure of the invention

The object of the invention is therefore to avoid the disadvantages of the prior art and to achieve a high compression and optimum smoothness in a rotary piston internal combustion engine with the least possible effort.

According to the invention the object is achieved in a rotary piston internal combustion engine of the type mentioned with a housing having an inner, epitrochoidal shell surface and a rotary piston with two arcuate piston skirt surfaces and two corners, characterized in that d) a separate combustion chamber in the housing with a passage to the interior in Area of the first jacket portion of the lateral surface is arranged. Furthermore, the object is achieved in a rotary piston internal combustion engine having at least two rotary pistons and a housing, each having an inner space for each rotary piston in which rotate the rotary piston, characterized in that in the housing a separate, central combustion chamber is provided for the interiors and all interiors and rotary pistons are arranged at each rotational position in a point symmetry with the center of the combustion chamber.

Furthermore, the object is achieved with a seal assembly of the type mentioned with a seal in a groove of the rotary piston characterized in that the seal has a contact body, which is pivotally provided in the groove via a support body, wherein the contact body with a contact surface touches the inner circumferential surface and the contact surface is in a region of the inner circumferential surface with this completely positive fit.

The object is also achieved with a sealing arrangement of the type mentioned above in that the seal contains steel wool or steel Gefiecht and at a contact surface to the inner surface of a film is provided. The principle of the rotary piston internal combustion engine according to the invention with an inner, epitrochoidal lateral surface and a rotary piston with two arcuate Kolbenmantelfiächen and two corners based on the fact that alternately rests one of the piston skirt surfaces in a certain rotational position completely on the inner circumferential surface of the housing. In other words, the rotary piston subdivides the interior space into two working spaces whose volume continuously changes between zero and a maximum value during a rotation. A defined between the Kolbenmantelfiäche and the epitrochoidal lateral surface compression space has in the above-mentioned rotational position only about the volume of the combustion chamber provided in this area. As a result, the compression ratio can be determined solely by the volume of the combustion chamber at a maximum volume of a working space given by the geometry. In this way, advantageously with a suitable shape of the combustion chamber and directly high compression ratios are possible. The inventive rotary piston internal combustion engine is suitable, for example, without a pre-compression directly for a diesel operation.

Another aspect of the invention relates to a rotary piston internal combustion engine having at least two rotary pistons and a housing, each having an interior space for every rotary piston. Due to the point-symmetrical arrangement of the interiors and rotary piston around the center of the central combustion chamber, the common center of gravity of the rotary piston is always in the center of the combustion chamber during a rotation. The inventive rotary piston internal combustion engine thus runs in principle soft and vibration-free. Additional balancing is avoided very efficiently. The two rotary pistons rotate point-symmetrically and in the same direction, whereby synchronization of their rotation is greatly simplified. The seal assembly according to the invention with a contact body, which is pivotally provided in the groove of the rotary piston via a support body, the seal between this and a piston skirt surface is improved in trochoidal lateral surfaces. The abutment body adapts to the ever-changing angle between the normal of the piston skirt surface and the normal of the inner shell surface of the housing during rotation by pivoting. With the positive engagement of the contact body in a region of the shell inner surface, this area can be particularly effective seal. In this way, for example, the seal in the region of a combustion chamber opening, an outlet or an inlet can be optimized. In this case, the bearing body can be dimensioned so that it completely closes these openings in a rotational position of the rotary piston.

The inventive seal assembly with steel wool or steel wire mesh, eg, knitted steel wool, braided steel wool or a combination thereof, and a foil, such as steel foil, utilizes a combination of the properties of these materials for a seal between the rotary piston and Innenmantelfiäche of the housing. Requirements for an optimal seal are in particular a high conformability and elasticity and a high speed of adaptation. The speed is determined by the speed of sound of the sealing material. By using a combination of steel wool or steel wire mesh with adjustable elasticity and a high speed film of sound, a quasi material is created for the gasket which optimizes the conformability and speed of adaptation to the geometry and other parameters of the rotary engine let adjust. An advantageous embodiment of the rotary piston internal combustion engine according to the invention with an epitrochoidal, inner circumferential surface and a rotary piston with two arcuate piston skirt surfaces and two corners is achieved in that the cross-sectional area of the passage is smaller than the cross-sectional area of the combustion chamber. By this measure, the time span in which a corner of the rotary piston is above the passage and thus a disadvantageous connection between the work chambers separated from the rotary piston, shortened. Furthermore, a complete closure of the passage can be realized by a seal on the rotary piston easier.

In an advantageous development of the rotary piston internal combustion engine according to the invention with an epitrochoidal, inner lateral surface and a triangular rotary piston, the housing contains at least two internal spaces each with a rotary piston and a separate, central combustion chamber for all internal spaces. In this case, the epitrochoid-shaped lateral surfaces of the interior spaces and the arc-shaped piston jacket surfaces are arranged in each rotational position in a point-symmetrical manner with respect to the center of the central combustion chamber. The common focus of the rotating rotary piston is therefore always in the center of the combustion chamber. A smooth and vibration-free running of the rotary piston internal combustion engine is achieved without further balancing measures solely by the given geometry. Although form oscillations and housing deformations during operation of the rotary piston internal combustion engine are not completely avoided, they always remain point-symmetrical and do not lead to vibrations of the rotary piston internal combustion engine as a whole.

In a preferred embodiment of the inventive rotary piston internal combustion engine with a two-cornered rotary piston, a sealing arrangement is provided for sealing the rotary piston against the trochoidal lateral surface of the housing at both corners of the rotary piston, which has a seal in a groove which runs parallel to the axis of rotation of the rotary piston. The seal has a contact body, which is provided via a support body pivotally in the groove. The body touches with a Anlagefiäche the inner circumferential surface, wherein the contact surface in the region of the combustion chamber is completely positive with the lateral surface. Depending on the angle between the longitudinal axis of the rotary piston and the normal of the epitrochoid-shaped lateral surface of the housing, the contact body optimally aligns itself by pivoting. Due to the positive locking of the contact body in the region of the combustion chamber, a particularly effective sealing takes place here. In this case, the contact body can be dimensioned so that it completely closes the passage of the combustion chamber.

An advantageous embodiment of the rotary piston internal combustion engine according to the invention is further achieved in that a respective sealing arrangement for sealing the rotary piston against the epitrochoidal lateral surface of the housing is provided at both corners of the rotary piston, which has a seal in a groove which is parallel to the axis of rotation of the rotary piston and wherein the seal contains steel wool or a Stahldrahtgefiecht and is provided at a contact surface to the lateral surface of a film. As already described above, by a combination of steel wool or steel wire mesh having different elasticity and a high-speed sounding film, a quasi-material for a gasket having a high conformability and a high speed of matching is realized. This is particularly important because of the relatively large change in the angle between the longitudinal axis of the rotary piston and the normal of the epitrochoidal shell surface in the rotary piston internal combustion engine according to the invention with a two-sided rotary piston. As a steel wool, for example, a suitably knitted or braided steel wool and a suitable sized steel foil can be used as a film.

In one embodiment of the invention, the film has holes through which a lubricant for lubricating the plant surface emerges. As a result, lubrication is advantageously carried out directly at the location where the Anlagefiäche and the inner surface of the housing touch. In doing so, an uninterrupted and sufficient supply of lubricant can be ensured via channels, which connect the holes with a container with lubricant. Further embodiments and advantages will become apparent from the subject of the dependent claims, as well as the drawings with the associated description.

An embodiment of the invention is explained below with reference to the accompanying drawings.

Brief description of the drawings

Fig. 1 shows a schematic schematic diagram of a section through a

Rotary piston internal combustion engine with a two-sided rotary piston.

2a-h show schematically eight views of successive rotational positions in two revolutions of the rotary piston of the rotary piston internal combustion engine according to FIG. 1.

3a, 3b show a schematic sectional view of a rotary piston internal combustion engine with two rotary pistons at two different rotational positions.

Fig. 4 shows a seal assembly for a rotary piston of a

Rotary piston machine, for example according to FIG. 1.

Fig. 5 shows a further seal arrangement for a rotary piston of a

Rotary piston machine, for example according to FIG. 1.

Preferred embodiment

In Fig. 1, 10 denotes a rotary piston internal combustion engine. The rotary piston internal combustion engine 10 includes a housing 12 with an inner epitrochoidal lateral surface 14. The lateral surface 14 extends along a single closed trochoidal arch, which is divided by an axis of symmetry II into two uniform semi-arches. Together with two side surfaces or cover surfaces not shown in FIG. 1, the lateral surface 14 encloses an interior 16 of the housing 12.

In the interior 16, a rotary piston 18 is arranged. The rotary piston 18 has two identical, arcuate Ko Ibenmantelflächen 20, 22, which together form a continuous lateral surface of the rotary piston. The piston skirt surfaces 20, 22 are arranged mirror-symmetrically to the longitudinal axis II-II of the rotary piston 18. By this arrangement, two corners 24, 26 of the rotary piston 18 are formed in its lateral surface, which are located at the same distance from the center or center of gravity 28 of the rotary piston 18 on the longitudinal axis II-II.

During a rotation in the interior 16, the rotary piston 18 rotates about its center 28, while at the same time the center 28 passes through a circle 32 with a radius r. The rotary piston 18 is connected thereto with an eccentric shaft 30 guided through one or both side surfaces of the inner space 16, a corresponding gear or other suitable device which guides the center of gravity 28 during rotation along the circle 32.

Geometrically, a circle 34 with a radius R = 2r rolls around the circle 32. During a rotation of the rotary piston 18, the corners 24, 26 pass exactly through the one closed trochoidal arch of the epitrochoid of the inner lateral surface 14 of the housing 12. The corners 24, 26 are always in contact with the epitrochoidal lateral surface 14 during a rotation of the rotary piston 18. Machines with such a geometry are also referred to as a 1: 2 rotary engine with slip engagement. The ratio 1: 2 of the radii of the circles 32, 34 is also directly in the geometry of the rotary piston internal combustion engine 10. The epitrochoid has a Trochoidbogen and the rotary piston 18 two corners 24, 26th

In general, the arc shape of the lateral surfaces of a rotary piston of a rotary piston machine, as initially described, results as an inner envelope of the pattern of the correspondingly rotating epitrochoid. In a 1: 2 rotary piston engine corresponds to Arched shape exactly a section of epitrochoid. Also in this embodiment, the two Kolbenmantelfiächen 22, 24 are formed so that they each rest in a rotational position of the rotary piston 18 at a portion of the epitrochoidal lateral surface 14. FIG. 1 shows the rotary piston 18 in a rotational position in which the piston skirt surface 22 rests completely positively on a first jacket section 36 of the epitrochoidal lateral surfaces 14. After half a rotation of the rotary piston 18 then the piston skirt surface 20 is completely against the first shell portion 36. In FIG. 1, the symmetry axis II-II divides the epitrochoidal lateral surface 14 into the first jacket section 36 and a second jacket section 38, in which only the corner 24 or the corner 26 abuts in all rotational positions. At both corners 24, 26 of the rotary piston 18, a sealing arrangement 40 described in more detail below is also provided.

The housing 12 includes an inlet passage 42 having an inlet valve 44 and an opening 46 to the interior 16. The inlet passage 42 serves to introduce air or a fuel-air mixture into the interior 16. The opening 46 of the inlet passage 42 is at the boundary between the first shell portion 36 and the second shell portion 38 in the first shell portion 36 or on the boundary between the first shell portion 36 and the second shell portion 38 is arranged.

On the inlet channel 42 with respect to the symmetry axis I-I opposite side of the housing 12, an outlet channel 48 with an outlet valve 50 and an opening 52 to the interior 16 is disposed in the housing. Burned exhaust gases are removed from the interior 16 through the outlet channel 48. The opening 52 of the outlet channel 48 is provided in the first jacket section 36 in the immediate vicinity of the second jacket section 38 or on the boundary between the first jacket section 36 and the second jacket section 38.

In the housing 12, a combustion chamber 54 is further included with a passage 56. The passage 56 connects the combustion chamber 54 to the interior 16 in the first shell portion 36 between the axis of symmetry II and the inlet channel 42. Preferably, the passage 56 is closer to the axis of symmetry II than to the inlet channel 42 in the first shell portion 36. In a preferred embodiment an axis of symmetry of the combustion chamber 54 and the symmetry axis II form an angle of approximately 30 °. The cross-sectional area of the passage 56 is smaller than the cross-sectional area of the combustion chamber 54. As a result, the passage 56 is swept faster by a corner 24, 26 during a rotation of the rotary piston 18 and can thereby be completely closed by a suitable sealing arrangement 40. In the combustion chamber 54 may not be shown in Fig. 1 injection device for fuel, such as diesel fuel, hydrogen or natural gas, may be provided. In Fig. 2a-h eight consecutive rotational positions in two revolutions of the rotary piston to illustrate the working cycles of the rotary piston internal combustion engine of FIG. 1 are shown. Like components are therefore designated by corresponding reference numerals. The rotary piston 18 rotates in Fig. 2a-h clockwise and divides the interior 16 into two working spaces 58, 60. The volume of both working chambers 58, 60 varies during a rotation of the rotary piston 18 between zero and a maximum value. In the following, the working space 58 will be considered in greater detail.

Starting from Fig. 2a, in which the rotary piston 18 rests with its one piston skirt surface 22 on the epitrochoidal lateral surface 14 of the housing 12 and thus the volume of the working chamber 58 is equal to zero, the rotary piston 18 rotates clockwise and passes through the position of FIG. 2b to reach after half a revolution, the position of Fig. 2c. The volume of the working space 58 increases from zero to its maximum value. During this intake stroke, the intake valve 44 is opened and air or a fuel-air mixture is sucked into the working space 58, arrow 62.

Subsequently, the rotary piston 18 continues to rotate beyond the rotational position in FIG. 2d to the position according to FIG. 2e. The rotary piston 18 has now performed a complete revolution. In this case, the volume of the working space 58 decreases from its maximum value and finally disappears in the position FIG. 2e. During this compression stroke, the exhaust valve 50 is closed and the air or fuel-air mixture is continuously compressed and eventually completely into the combustion chamber 54 pressed. The compression ratio of the rotary piston internal combustion engine 10 thus results from the volume of the combustion chamber 54 and the maximum value of the volume of the working chamber 58, 60. In the position of Fig. 2e is an ignition, arrow 64, the fuel-air mixture or auto-ignition an injected fuel, such as diesel fuel or hydrogen. An injection of the fuel may be made shortly before, if an injector and a suction of air are provided. The combustion gases expand and push the rotary piston 18 through the rotational position in Fig. 2f to that in Fig. 2g. The volume of the working space 58 rises again in this working cycle up to its maximum value. The inlet valve 44 is closed in this process.

Finally, from the rotational position in FIG. 2g to the position shown in FIG. 2h, the volume of the working space 58 is decreased again. The exhaust gases are discharged from the working space via the opened outlet valve 50, arrow 66. The exhaust stroke is as the last of the four strokes of the rotary piston internal combustion engine upon re-reaching the rotational position Fig. 2a and thus after two revolutions of the rotary piston 18 finished. In the other working space 60, a time-shifted work cycle with 4 cycles can take place during the described work cycle.

Due to the separate combustion chamber 54 and the 1: 2 rotary piston geometry used, the compression ratio of the rotary piston internal combustion engine 10 at a given maximum value of the volume of the working chambers 58, 60 determined only by the volume of the combustion chamber 54. The compression ratio can therefore be determined over a very large range by a corresponding dimensioning of the combustion chamber 54. Diesel operation becomes directly possible without precompression stage. FIGS. 3a and 3b show a rotary piston internal combustion engine 100 with two rotary pistons 102, 104 in two different rotational positions. The first rotary piston 102 rotates in a first inner space 106 and the second rotary piston 104 in a second inner space 108. The rotary pistons 102, 104 have identical shapes and also the interiors 106, 108 are uniform. The interior spaces 106, 108 are arranged in a housing 110. In the housing 110, a separate, central combustion chamber 112 is also included. The combustion chamber 112 has a first passage 114 to the first interior 106 and a second passage 116 to the second interior 108 and thus simultaneously serves as a combustion chamber 112 for both interior spaces 106, 108 with the rotary piston 102, 104. In other embodiments, three or more uniform rotary piston may be arranged in each uniform internal spaces around a central combustion chamber. For this purpose, the combustion chamber would have a corresponding number of passages to each interior.

The shape of the rotary pistons 102, 104 and the inner spaces 106, 108 is identical in this embodiment with that of the rotary piston 18 and the interior 16 of the rotary piston internal combustion engine 10 of FIG. The rotary pistons 102, 104 thus each have two uniform corners 118 and two similar, arcuate piston skirt surfaces 120. Both inner spaces 106, 108 contain identically shaped, epitrochoidal lateral surfaces 122. A rotary piston 102, 104 thus forms, together with the corresponding inner space 106, 108, a 1: 2 rotary piston geometry. Other components of the internal combustion engine 100 and the operation substantially correspond to those of the rotary piston internal combustion engine 10 of FIG. 1 and FIG. 2a-h and have already been described.

The inner chambers 106, 108 and the rotary pistons 102, 104 are each arranged so that they are point-symmetrical in each rotational position to the center 124 of the combustion chamber 112. In this case, other rotating components of the rotary piston internal combustion engine, such as an eccentric shaft or a corresponding gear, also have this Punksymmetrie. Due to the point symmetry, the direction of rotation of the rotary pistons 102, 104 is determined. Both rotary pistons 102, 104 rotate in the same direction and corresponding corners 118 and piston skirt surfaces 120 of the rotary pistons 102, 104 are always arranged point-symmetrically to the center 124. This can be clearly seen in Fig. 3b in comparison with Fig. 3a. In Fig. 3b, the rotary piston 102, 104 have rotated relative to Fig. 3a by a quarter turn. In alternative embodiments, the point-symmetrical arrangement of the internal spaces and the rotary piston to the center of a central combustion chamber in rotary piston internal combustion engines with a different geometry, such as 2: 3 or 4: 5 rotary engines with slipping engagement realized.

As a result of the punctiform symmetrical arrangement, the common center of gravity of the rotary pistons 102, 104 is always at the center 124 of the combustion chamber 112 during a rotation. The rotary piston internal combustion engine 100 therefore runs vibration-free and quiet. Additional balancing is efficiently avoided.

4 shows a sealing arrangement 210 for sealing a rotary piston against a trochoid-shaped inner lateral surface of a housing. FIG. 4 shows a section of a rotary piston 212 with a piston skirt surface 214 in a plan view. In the rotary piston 212, a groove 216 is provided parallel to the rotation axis of the rotary piston 212. The groove 216 divides the piston skirt surface 214 in two Ko Ibenmantelflächen. The groove 216 is formed by two lugs 218 and a circular recess 220 in the rotary piston 212.

In the groove 216, a seal 222 is arranged. The seal 222 has a contact body 224 and a carrier body 226 connected thereto. The carrier body 226 contains a circular bulge 228, which is arranged in a form-fitting and rotatable manner in the circular recess 220 of the groove 216. Furthermore, the carrier body 226 includes a neck 230, which protrudes from the groove 216 and carries the contact body 224. The contact body 224 has a contact surface 232 which contacts a trochoid-shaped inner lateral surface of a housing. Here, the contact surface 232 is formed so that it is completely positive fit in a region of the trochoid-shaped inner circumferential surface with this. In the area of the lugs 218, recesses 234 are provided in the piston skirt surface 214. The recesses 234 are adapted to receive an arm of the abutment body 224 upon pivoting of the seal 222.

As a result of the described rotatable reception of the carrier body 226 in the groove 216, the contact body 224 is predetermined by one of the lugs 218 and the neck 230 Region opposite the groove 216 pivotally. In this case, a part of the contact body 224 is received by one of the recesses 234. The abutment body 224 adapts to the constantly changing angle between the normal of the jacket surface 214 and the normal of the trochoid-shaped inner circumferential surface of the housing upon rotation of the rotary piston 212. In this case, the selectable area of the trochoid-shaped inner circumferential surface, which corresponds to the shape of the contact surface 232, is particularly effective in sealing. Also, the size of the contact body 224 and thus the contact surface 232 can be adjusted within limits of openings of the inner circumferential surface. In this way, a complete closure of an opening through the seal 222 in a ration position is possible.

The seal assembly 210 of Fig. 4 is particularly suitable for the rotary piston internal combustion engine 10 of FIG. 1 for sealing the corners 24, 26 opposite the epitrochoidal lateral surface 14. The seal assembly 210 is arranged in each corner 24, 26 of the rotary piston 18 and the Bearing surface 232 preferably has the shape of the epitrochoidal lateral surface 14 in the region of the passage 56 of the combustion chamber 54. In addition, the contact surface 232 is sufficiently dimensioned in order to be able to completely close the passage 56. As a result, when the corners 24, 26 are passed over, a complete sealing of the passage 56 takes place. A disadvantageous connection between the two working spaces 58, 60 (see FIG. 2b) via the passage 56 is prevented in this rotational position.

FIG. 5 illustrates another sealing arrangement 250 for a rotary piston of a rotary piston machine for sealing the rotary piston against a trochoid-shaped inner lateral surface of a housing. FIG. 5 shows a section of a rotary piston 252. The rotary piston 252 has a piston skirt surface 254. In the rotary piston 252, a groove 256 is provided parallel to the axis of rotation of the rotary piston 252. The groove 256 divides the piston skirt 254 in two Kolbenmantelfiächen.

In the groove, a seal 258 is arranged. The gasket 258 includes steel wool 260 or a steel wire mesh that has been appropriately processed to achieve a desired elasticity. For example, a knitted, braided or woven steel wool or a suitably processed steel wire. For example, appropriately knitted, braided or woven steel wool may be used. The steel wool 260 is partially or entirely surrounded by a steel foil 262. Also, the steel foil 262 is selected for rigidity according to the requirements. A portion of the steel foil 262 forms a contact surface 264. This Anlagefiäche 264 is at a rotation of the rotary piston 252 on the trochoidal inner surface of the housing and seals the rotary piston 252 from the inner circumferential surface. When sliding along the inner circumferential surface, the seal 258 fits the curvature of its contact surface 264 of the curvature of the respective location of the lateral surface sufficiently quickly.

The steel foil 262 has holes 266 in the region of the contact surface 264 through which a lubricant for lubricating the contact surface 262 emerges. The lubricant is passed through the porous steel wool 260 or the steel wire bonded to the holes 266. Alternatively or additionally, channels not shown in Fig. 5 are provided for connecting the holes 266 with a lubricant container. Through the channels, the lubricant is guided to the holes 266. The space occupied by the steel wool can also serve as such a channel. By combining the steel wool 260 or the steel wire body with the steel foil 262, a quasi material is created for the gasket 258 which has the high elasticity of the steel wool 260 and the great adaptability of the steel foil 262 due to its rigidity. The elasticity and the stiffness can be varied depending on the steel wool 260 and steel foil 264 used and adapted to the conditions of use, in particular a geometry of the rotary piston machine. The seal 258 thus has conformability and speed of adjustment that optimally adapts to the geometry and other parameters of the rotary piston engine. The sealing arrangement 250 is therefore particularly suitable for the rotary piston internal combustion engine 10 according to FIG. 1 for sealing the corners 24, 26 with respect to the epitrochoidal lateral surface 14. Furthermore, the sealing arrangement 250 is also suitable for any volume-displacing rotary machine, in particular Wankelmaschinen, as well as for end faces of all prismatic machines and also for reciprocating engines.

Claims

claims

A rotary piston internal combustion engine (10), comprising a) a housing (12) with an inner, epitrochoidal lateral surface (14) along a single closed Trochoidbogen, wherein the lateral surface (12) together with two side surfaces of an interior (16) of the housing ( 12), b) a rotary piston (18) having two arcuate Ko Ibenmantelflächen (20, 22) which are arranged symmetrically to the longitudinal axis (II-II) of the rotary piston (18) and two corners (24, 26) of the rotary piston (18 ) on the longitudinal axis of the rotary piston (18) form, and c) the rotary piston (18) in the interior (16) rotates and thereby rotates about its center (28), while the center (28) passes through a circular path (32) Both corners (24, 26) during rotation constantly abut the epitrochoidal lateral surface (14) and both arcuate piston skirt surfaces (20, 22) are formed so that each in each case in a certain rotational position positively a first jacket section (36) of the jacket surface (14), characterized in that d) a separate combustion chamber (54) in the housing (12) with a passage (56) to the interior (16) in the region of the first jacket section (36) the lateral surface (14) is arranged.

2. rotary piston internal combustion engine (10) according to claim 1, characterized in that the cross-sectional area of the passage (56) is smaller than the cross-sectional area of the combustion chamber (59).

3. rotary piston internal combustion engine (10, 100) according to claim 1 or 2, characterized in that the housing (12, 110) at least two interior spaces (106, 108) each having a rotary piston (102, 104) and a separate, central combustion chamber (112) for all internal spaces (106, 108), wherein the epitrochoidal lateral surfaces (122) of the inner spaces (106, 108) and the arcuate piston skirt surfaces (120) are arranged in each rotational position punctiform symmetrically to the center (124) of the central combustion chamber (112) are.

4. rotary piston internal combustion engine (10) according to one of claims 1 to 3, characterized in that in each case a sealing arrangement (210) for sealing the rotary piston (18) relative to the epitrochoidal lateral surface (14) of the housing (12) at both corners (24 , 26) of the rotary piston (18) is provided, which has a seal (222) in a groove (216) which is parallel to the axis of rotation of the rotary piston (18), wherein the seal (222) has a bearing body (224), which via a carrier body (226) is pivotally provided in the groove (216), the contact body (224) with an Anlagefiäche (232) touches the lateral surface (14) and the contact surface (232) in the region of the combustion chamber (54) completely with the Lateral surface (14) is form-fitting.

5. rotary piston internal combustion engine (10) according to one of claims 1 to 4, characterized in that in each case a sealing arrangement (250) for sealing the rotary piston (18) relative to the epitrochoidal lateral surface (14) of the housing (12) at both corners (24 , 26) of the rotary piston (18) is provided which has a seal (258) in a groove (256) parallel to the axis of rotation of the rotary piston (18), the seal (258) being a steel wool (260) or steel wire mesh contains and at a contact surface (264) to the lateral surface (14) a film (262) is provided.

6. rotary piston internal combustion engine (10) according to claim 5, characterized in that the film (262) has holes (266) through which a lubricant for lubricating the contact surface (264) emerges.

7. rotary piston internal combustion engine (10) according to claim 6, characterized in that the holes (266) is connected via channels with a container with the lubricant.

8. rotary piston internal combustion engine (100), comprising at least two rotary pistons (102, 104) and a housing (110) each having an inner space (106, 108) for each rotary piston (102, 104), in which the rotary piston (102, 104 ), characterized in that in the housing (110) a separate, central combustion chamber (112) for the internal spaces (106, 108) is provided and all internal spaces (106, 108) and rotary piston (102, 104) at each rotational position punksymmetrisch to the center (124) of the combustion chamber (112) are arranged.

A seal assembly (210) for a rotary piston (212) of a rotary piston machine for sealing the rotary piston (212) against a trochoidal inner surface of a housing upon rotation of the rotary piston (212) having a seal (222) in a groove (216) parallel to the axis of rotation of the rotary piston (212), characterized in that the seal (222) has a contact body (224) which is pivotally provided in the groove (216) via a carrier body (226), wherein the contact body (224) with a contact surface (232) touches the inner lateral surface and the contact surface (232) in a region of the inner lateral surface is completely positive with this.

A seal assembly (250) for a rotary piston (252) of a rotary piston machine for sealing the rotary piston (252) against a trochoidal inner surface of a housing upon rotation of the rotary piston (252) having a seal (258) in a groove (256) parallel to the axis of rotation of the rotary piston (252) passes, thereby in that the seal (258) contains a steel wool (260) or a steel wire mesh and a foil (262) is provided at a contact surface (264) to the inner surface of the shell.

A seal assembly (250) for a rotary piston (252) of a rotary piston machine according to claim 10, characterized in that the foil (262) has holes (266) through which a lubricant for lubricating the abutment surface (264) exits.

Seal assembly (250) for a rotary piston (252) of a rotary piston machine according to claim 11, characterized in that the holes (266) is connected via channels with a container with the lubricant.