WO2005017319A1 - Machine a piston rotatif annulaire - Google Patents

Machine a piston rotatif annulaire Download PDF

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Publication number
WO2005017319A1
WO2005017319A1 PCT/EP2004/008127 EP2004008127W WO2005017319A1 WO 2005017319 A1 WO2005017319 A1 WO 2005017319A1 EP 2004008127 W EP2004008127 W EP 2004008127W WO 2005017319 A1 WO2005017319 A1 WO 2005017319A1
Authority
WO
WIPO (PCT)
Prior art keywords
piston
valve
opening
separating
piston chamber
Prior art date
Application number
PCT/EP2004/008127
Other languages
German (de)
English (en)
Inventor
Wolf-Rüdiger Sauer
Original Assignee
Sauer & Gellersen Gbr
Sauer, Christian
Gellersen, Heinz
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Sauer & Gellersen Gbr, Sauer, Christian, Gellersen, Heinz filed Critical Sauer & Gellersen Gbr
Publication of WO2005017319A1 publication Critical patent/WO2005017319A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/18—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • F01C21/183—Arrangements for supercharging the working space
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C11/00—Combinations of two or more machines or engines, each being of rotary-piston or oscillating-piston type
    • F01C11/002—Combinations of two or more machines or engines, each being of rotary-piston or oscillating-piston type of similar working principle
    • F01C11/004—Combinations of two or more machines or engines, each being of rotary-piston or oscillating-piston type of similar working principle and of complementary function, e.g. internal combustion engine with supercharger
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C3/00—Rotary-piston machines or engines with non-parallel axes of movement of co-operating members
    • F01C3/02—Rotary-piston machines or engines with non-parallel axes of movement of co-operating members the axes being arranged at an angle of 90 degrees
    • F01C3/025—Rotary-piston machines or engines with non-parallel axes of movement of co-operating members the axes being arranged at an angle of 90 degrees of intermeshing engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing

Definitions

  • the invention relates to a piston machine for use as a pump, compressor or heat engine, in particular an internal combustion engine, with a working piston movably arranged in a piston chamber of a machine housing, and with closable suction and outlet openings for a working fluid.
  • the object of the invention is to provide a piston machine of the type mentioned in the introduction, in which the acceleration forces acting on the piston can be better controlled than in the prior art.
  • the machine housing comprises a piston chamber housing which encloses an essentially toroidal piston chamber, that at least one piston can be moved in a circular manner in the piston chamber and that the piston housing is provided with separating valves for periodically separating piston chamber segments, the separating valves being provided with the piston movement are synchronized. Due to the circularly rotating pistons, centrifugal forces essentially only occur relatively well under control. Because of the separating valves, compression or expansion spaces can be separated in the piston chamber, the separation being canceled by the synchronization of the separating valves according to the invention whenever the piston passes the separating valve.
  • the piston machine according to the invention can be used as a pump for liquids and gases or as a compressor for gases.
  • the piston engine according to the invention can be used as an internal combustion engine. It can also be used as a heat pump or hot air motor.
  • the piston chamber housing is provided on its radially inner side with a circumferential annular gap and that the piston or pistons is / are attached to the radially outer edge of a piston wheel which is provided with a disk-ring-shaped section in the Annular gap of the piston chamber protrudes and sits with its axis of rotation on a drive shaft.
  • the arrangement of the piston wheel according to the invention makes it possible to transmit the kinetic energy of the piston or pistons to the drive shaft.
  • the disk-shaped section of the piston wheel serves to seal the circumferential annular gap of the piston chamber housing.
  • the piston wheel is disk-shaped, it can be produced in a particularly simple manner. A disc ring-shaped section is thus included without any special effort. However, other conceivable embodiments can also have a disk with openings, as long as a disk-ring-shaped gate remains in the radially outer edge region. On the other hand, the piston wheel can also be designed as a spoke wheel.
  • the isolating valves in a valve housing have rotatably arranged, perforated valve disks which protrude essentially in the radial direction into the piston chamber and, depending on the angle of rotation, close a piston chamber segment or expose a through opening for the piston.
  • the construction and synchronization of the isolating valves with the pistons is extremely simple.
  • the isolation valves open and close by simply turning the valve disks in one direction at a time. If the openings in the valve disks coincide with the piston chamber, a through opening is created for the piston. Otherwise the piston chamber is separated into piston chamber segments at the location of the valve disc.
  • the synchronization with the piston takes place in a simple manner, for example by means of a gear transmission, which in particular transmits the rotary movement of the drive shaft with a suitable transmission ratio to the rotary movement of the valve disks.
  • a piston be arranged on the piston wheel and a separating valve synchronized with the drive shaft on the piston chamber housing, and an intake opening and an outlet opening before the separating valve in the direction of movement of the piston. Because of the simple design with a single piston and with a single Isolating valve, this embodiment is particularly suitable for inexpensive compressors or pumps.
  • an alternative embodiment is recommended, which is characterized by the measures that three separating valves arranged at equal angular intervals are provided, and that in the direction of movement of the pistons, a suction opening is provided after the first and second separating valve that before An overflow opening is provided in each case for the second and third separation valve, that an inlet opening is provided after the second separation valve, that the two overflow openings and the inlet openings are each closable by an overflow valve synchronized with the drive shaft and are connected to one another by a common overflow channel, and in front of the first separation valve an outlet opening is provided.
  • two of the three pistons each work as a compressor for compressing fresh air, which reaches the combustion chamber via the common overflow channel and the inlet opening. Because of the double number of compressing pistons, a higher compression can be achieved.
  • each of the two piston chamber housings each have a separating valve synchronized with the drive shaft and two piston wheels each arranged on the common drive shaft a piston that the separating valves and the pistons are each arranged at an angle of rotation of approximately 20 ° to 30 ° to one another, that in the direction of movement of the pistons after the separating valve of the first piston chamber housing, an intake opening and before the separating valve a closable by an overflow valve synchronized with the drive shaft
  • Overflow opening is provided, which leads into an overflow channel, which opens into an inlet opening of the second piston chamber housing, which is arranged after the second isolating valve, and that an outlet opening, which can be closed by an outlet valve synchronized with the drive shaft, is arranged in front of
  • Figure 1 is a schematic representation of a piston wheel according to the invention with three pistons;
  • Figure 2 is a schematic representation of a toroidal piston chamber housing with a radially inner annular gap
  • FIG. 3 a section S1 according to FIG. 6a of a section of the piston chamber housing with a cut-off valve;
  • FIG. 4 shows a sectional illustration of a piston chamber housing of a piston machine according to the invention that can be used as a compressor or pump;
  • Figure 5 ad an alternative embodiment of a piston machine usable as a pump or compressor with three pistons in four phases a - d
  • Figure 6 ag sectional views of a piston engine according to the invention in a first embodiment as an internal combustion engine in seven different phases a - g;
  • Figure 7 a-d a piston machine in a second embodiment as an internal combustion engine, in four phases a - d;
  • Figure 8 is a schematic, three-dimensional representation of a piston engine in a third embodiment as an internal combustion engine with two toroidal piston chamber housings;
  • FIG. 1 shows a disk-shaped piston wheel 4, on the radially outer edge of which three pistons 2a, 2b, 2c are attached.
  • a drive shaft 3 is arranged in the axis of rotation of the writing wheel 4.
  • FIG. 2 shows a toroidal piston chamber housing 1, which is provided on its radially inner side with a circumferential annular gap 16 which is intended to receive the radially outer disk-shaped area of the piston wheel 4, so that the pistons 2 are located in the toroidal piston chamber 17 of the piston chamber housing 1 can move in a circle.
  • Figure 3 is a partial view of an inventive
  • Piston chamber housing 1 is shown in section S1 according to FIG. 6a, the drive shaft 3, the piston wheel 4 and a piston 2 being recognizable. Furthermore, a separating valve 10 is shown which has a valve disk 18 which can be rotated about a valve shaft 19 and which is provided with an opening 20 for the passage of the piston 2.
  • Direction of rotation 21 of the valve disk 18 is indicated by an arrow.
  • 4 shows the piston chamber housing 1 and the piston wheel 4 arranged therein, which here is only equipped with a single piston 2.
  • the direction of rotation 22 of the piston wheel 4 around the drive shaft 3 is indicated by the arrow.
  • the single isolating valve 10 rotates about the valve axis 19 and is currently in an open state, the piston 2 passing freely through the breakthrough of the valve disk 18, not shown.
  • the piston machine shown in FIG. 4 can be used as a compressor for gases or as a pump for conveying gases or liquids.
  • the function in the compression of gases is described below as an example.
  • the piston 3 sweeps over the suction opening 6 in the direction of rotation 22, the separating valve 10 closing, so that a separated piston chamber segment is formed between the separating valve 10 and the piston 2.
  • the piston wheel 4 When the piston wheel 4 is rotated further in the direction of rotation 22, said piston chamber segment increases, gas being sucked in through the suction opening 6.
  • the piston wheel 4 When the piston wheel 4 has completed almost a complete revolution, the piston 2 sweeps over the outlet opening 9.
  • the outlet opening is equipped with a check valve (not shown), so that although gas can be pushed outwards, no gas can get into the piston chamber 17 from the outside , While the piston 2 sweeps over the outlet opening 9, the isolating valve 10 opens the passage, so that the piston 2 returns to the in
  • Figure 4 reached position.
  • the entire piston chamber 17 is now filled with sucked-in gas, which is pushed in front of the piston 2 when the piston wheel 4 rotates further in the direction of rotation 22.
  • Isolating valve 10 closes again, the piston 2 pushes the gas in the piston chamber segment located in front of it in the direction of rotation 22 through the outlet opening 9 out of the piston chamber 17, while at the same time it sucks fresh gas through the suction opening 6 on its rear side.
  • the gas can thus be compressed by the piston 2 in the segment of the piston chamber 17 located in front of the piston and can be conveyed outside through the outlet opening 9.
  • FIGS. 5 a - d functions in a similar manner for compressing gas or conveying gas or liquid.
  • the difference from FIG. 4 is that three pistons 2a, 2b, 2c are now arranged on the piston wheel 4 and three separating valves 10a, 10b, 10c are arranged on the piston chamber housing 1.
  • the three separating valves 10a, 10b, 10c enable the piston chamber 17 to be subdivided into piston chamber segments 17a, 17b, 17c.
  • the operation of the piston machine according to FIG. 5 is described below with the aid of the piston 2a, the other two pistons 2b and 2c working in accordance with the piston 2a, which leads to a tripling of the delivery rate.
  • FIG. 5a The initial situation can be found in FIG. 5a, where, for example, the piston 2b has performed a suction process in the piston chamber segment 17a.
  • the pistons 2a, 2b, 2c have passed the isolation valves 10a, 10b, 10c and the isolation valves 10a, 10b, 10c are closed.
  • the pistons push further counterclockwise, for example the piston 2a in the piston chamber segment 17a towards the outlet opening 9a, the fresh gas previously sucked into the piston chamber segment 17a by the piston 2b being compressed and under pressure by the Exhaust opening 9a is pushed out.
  • Parallel and analogous processes take place in the piston chamber segments 17b and 17c.
  • the outlet openings 9a, 9b, 9c are provided with check valves, not shown, so that the compressed gas can only be expelled there, but cannot flow back into the respective piston chamber segment 17a, 17b, 17c.
  • a first embodiment of the piston machine according to the invention as an internal combustion engine is explained in more detail in FIGS. 6a to 6g.
  • the piston wheel 4 moves counterclockwise in the direction of rotation 22.
  • Piston chamber housing 1 two separating valves 10, 11 are arranged at an angular distance of approximately 120 ° to one another. In the direction of movement of the pistons 2a, 2b, 2c there is an outlet opening 9 in front of the separating valve 11 and then an intake opening 12. In front of the other separating valve 10 there is an overflow opening 13 which is connected to an inlet opening 26 via an overflow channel 14 indicated by dashed lines.
  • An overflow valve 5, which is intended to open and close the inlet opening 26, is arranged directly on the inlet opening 26.
  • the overflow valve 5 has a valve disk 25 with an opening 24.
  • the rotation of the valve disk 25 is synchronized with the rotation of the drive shaft 3.
  • the overflow valve 5 does not fundamentally differ in structure and synchronization from the isolating valves 10, 11. The only differences are in the shape of the opening 20 or 25 and in the arrangement of the respective valves. In the field of
  • a combustion chamber 15 is provided in the inlet opening 26 and is arranged radially outside the piston chamber 17.
  • a spark plug 7 and an injection nozzle 8 for injecting fuel are also arranged on the combustion chamber 15.
  • Pistons 2a, 2c can pass.
  • the isolating valves 10, 11 are then closed again, the situation shown in FIG. 6c occurring.
  • the piston 2a will now open the suction opening 12 on its further path and suck in fresh air from the suction opening 12. This situation is shown in Figure 6d.
  • the piston 2a has reached the overflow opening 13.
  • the two separating valves 10, 11 are opened again so that the pistons 2a, 2b can pass.
  • the separating valve is in the position of the piston 2a shown in FIG.
  • Combustion chamber 15 happens. At this moment, the overflow valve 5 opens, so that compressed fresh air from the overflow channel 14 reaches the combustion chamber 15, where fuel is injected and ignited.
  • the piston 2a has passed the suction opening 12, as a result of which a space with fresh air is partitioned between the piston 2a and the piston 2b, which the piston 2b previously sucked in through the suction opening 12.
  • the isolation valve 10 has opened so that the piston 2b can pass. At the same time, it releases the overflow opening 13.
  • the isolation valve 10 will close, so that the fresh air located between the isolation valve 10 and the piston 2a is compressed by the further movement of the piston 2a until the piston 2a reaches the position shown in FIG. 6e, in which it reaches the overflow opening 13 covers and closes.
  • the compressed air is briefly stored in the overflow channel 14.
  • the overflow opening 13 is provided with a valve, not shown, which prevents the compressed fresh air from flowing back into the piston chamber 17.
  • a valve not shown, which prevents the compressed fresh air from flowing back into the piston chamber 17.
  • FIGS. 7a-d A second embodiment of the piston machine according to the invention as an internal combustion engine is shown in FIGS. 7a-d.
  • a piston wheel 4 arranged on a drive shaft 3 three pistons 2a, 2b, 2c arranged at equal angular intervals of 120 °.
  • Three isolating valves 10a, 10b, 10c are arranged on the piston chamber housing 1.
  • the piston chamber housing 1 is provided with three overflow valves 5a, 5b, 5c, each of which has a valve disk 25.
  • the valve disks 25 rotate counterclockwise in the direction of rotation 21 and are synchronized with the rotation of the piston wheel 4 in the direction of rotation 22.
  • the valve disks 18 of the isolating valves 10a, 10b, 10c are also synchronized with the rotation of the piston wheel 4.
  • the inlet opening 26 is connected via a modified overflow channel 23 both to the overflow opening 13a and to the overflow opening 13c.
  • Overflow valve 5c is just open, because the opening 24c of the valve disk 25 is currently coincident with the inlet opening 26.
  • fuel is injected into the space between the third isolating valve 10c and the piston 2a and then through an injection nozzle (not shown) by means of a not Spark plug shown ignited so that the piston 2a is driven towards the first isolation valve 10a.
  • the two pistons 2b and 2c suck in fresh air on their rear through the two suction openings 12a and 12b.
  • the pistons 2b and 2c compress on their front side the fresh air sucked in by the pistons 2c and 2a during the previous 120 ° rotation of the piston wheel 4.
  • the second embodiment of the internal combustion engine according to FIGS. 7a-d has the advantage over the first embodiment that two pistons are always involved in the compression process, as a result of which a higher compression of the fresh air drawn in can be achieved before the fuel is injected and ignited.
  • two piston chamber housings 1a, 1b are provided, in each of which a separating valve 10a, 10b is arranged.
  • the two toroidal piston chamber housings 1a, 1b are arranged on the same axis of a drive shaft 3 at an axial distance from one another.
  • the drive shaft 3 is not shown in FIG. 8.
  • An overflow channel 27 is arranged between the two piston chamber housings 1a and 1b.
  • a piston wheel 4a is arranged on the piston chamber housing 1a and a piston wheel 4b on the piston chamber housing 1b each on a common drive shaft 3.
  • the piston wheels 4a, 4b rotate counterclockwise in the direction of rotation 22.
  • both the separating valves 10a, 10b and the two pistons 2a, 2b are each arranged at an angle of approximately 25 ° to one another in the direction of rotation 22.
  • An overflow valve 5a is also arranged on the piston chamber housing 1a and an overflow valve 5b is arranged on the piston chamber housing 1b.
  • the piston chamber housing 1 a has an intake opening 6, while the piston chamber housing 1 b is provided with an outlet opening 9.
  • the piston chamber housing 1a serves as a compressor for fresh air drawn in.
  • the piston 2a sucks fresh air through its suction opening 6 on its rear side, which is at the back in the direction of movement, and at the same time compresses the fresh air previously sucked in on its front side to press into the overflow channel 27.
  • the overflow valve 5a clears the way to the overflow channel 27.
  • the overflow valve 5a then closes and the isolating valve 10a is opened so that the piston 2a can pass the overflow channel 27, the isolating valve 10a and the suction opening 6.
  • the isolating valve 10a is then closed again and the suction or compression process in the piston chamber housing 1a begins again.
  • the working stroke and exhaust stroke of the internal combustion engine take place simultaneously in the piston chamber housing 1b.
  • the isolation valve 10b is closed.
  • the overflow valve 5b is opened briefly in order to allow compressed fresh air from the overflow channel 27 to flow into the small combustion chamber between the rear of the piston 2b, which is at the back in the direction of movement 22, and the isolating valve 10b.
  • fuel is injected through an injection nozzle (not shown) and ignited by means of a spark plug (not shown), whereby the piston 2b is driven counterclockwise.
  • the burning fuel-air mixture relaxes and does work on the piston 2b, which is transmitted to the drive shaft 3.
  • the piston 2b pushes the burned exhaust gas out of the previous revolution through the outlet opening 9 on its front side.
  • the piston 2b can pass through the outlet opening 9, the isolation valve 10b and the overflow channel 27. After that, the work cycle on the rear of the piston 2b and the exhaust cycle on its front run again.
  • FIG. 9c shows the interaction of the two pistons 2a and 2b as well as the two separating valves 10a, 10b and the overflow channel 27 between them with the two overflow valves 5a and 5b.
  • the piston machine according to the invention has the advantage, in particular in its design as an internal combustion engine, that the energy contained in the hot combustion gases can be converted into mechanical work far more effectively, since the gases can be expanded further in the engine according to the invention than in the reciprocating piston engine.
  • the largest possible stroke of the piston machine is limited to about 1.5 times the piston diameter, because otherwise the laterally deflecting connecting rod would conflict with the guidance of the piston, ie the cylinder wall.
  • the piston can travel a great deal more distances during the expansion process, depending on the present embodiment.
  • the piston can move by more than 300 °, which corresponds to approximately 15 times the piston diameter.
  • the combustion gases can expand about 10 times as much as with the reciprocating piston machine.
  • the work done in the piston machine according to the invention is additionally transferred to the piston and the drive shaft instead of disappearing uselessly in the exhaust.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)

Abstract

L'invention concerne une machine à piston rotatif annulaire s'utilisant comme pompe, comme compresseur ou comme moteur thermique, notamment comme moteur à combustion interne, qui comprend un piston de travail (2) monté mobile dans une chambre de piston (17) de carter de moteur, ainsi que des ouvertures d'aspiration (6) et des sorties de décharge (9) pouvant être obturées, pour un fluide de travail. L'invention vise à améliorer ladite machine à piston rotatif. A cet effet, le carter du moteur comprend un carter de chambre de piston (1), qui renferme une chambre de piston (17) sensiblement toroïdale. Au moins un piston (2) peut être déplacé en continu de manière circulaire dans la chambre de piston (17) et le carter de chambre de piston (1) est muni de clapets de séparation (10) pour séparer périodiquement les segments de la chambre de piston (17a, 17b, 17c). Lesdits clapets de séparation (10) sont synchronisés avec le mouvement des pistons.
PCT/EP2004/008127 2003-08-02 2004-07-21 Machine a piston rotatif annulaire WO2005017319A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE20312163 2003-08-02
DE20312163.5 2003-08-02

Publications (1)

Publication Number Publication Date
WO2005017319A1 true WO2005017319A1 (fr) 2005-02-24

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ID=34178069

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2004/008127 WO2005017319A1 (fr) 2003-08-02 2004-07-21 Machine a piston rotatif annulaire

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DE (1) DE10354621A1 (fr)
WO (1) WO2005017319A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2438859A (en) * 2006-06-05 2007-12-12 Juan Zak Toroidal fluid machine
RU2675639C2 (ru) * 2017-02-14 2018-12-21 Евгений Михайлович Пузырёв Роторно-винтовая машина

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2402974A (en) * 2003-06-17 2004-12-22 Richard See Rotary device in which rotor has sectors of different radii
US7341041B2 (en) * 2004-10-22 2008-03-11 Vgt Technologies Inc. Toroidal engine with variable displacement volume
US7305963B2 (en) * 2005-05-13 2007-12-11 Juan Zak Blade-thru-slot combustion engine, compressor, pump and motor

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US1704254A (en) * 1926-05-15 1929-03-05 Jaffe John Motor
JPS54129211A (en) * 1978-03-30 1979-10-06 Hachirou Hayashida Disc engine
GB2104154A (en) * 1981-08-20 1983-03-02 Sebastiano Italia Rotary positive-displacement fluid-machines
DE3825365A1 (de) * 1988-07-26 1990-02-01 Armin Mylaeus Drehkolbenmaschine
DE29522008U1 (de) * 1995-01-19 1999-07-29 Raab, Anton Gerhard, 80686 München Kraftmaschine

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US1836469A (en) * 1928-01-18 1931-12-15 Charles W Hill Engine
FR864566A (fr) * 1939-03-30 1941-04-30 Moteur rotatif à explosions
US2273625A (en) * 1939-09-23 1942-02-17 Thomas G Concannon Internal combustion engine
US2944533A (en) * 1954-09-22 1960-07-12 Park Robert Edward Internal combustion engine
DE1155286B (de) * 1957-07-03 1963-10-03 Reinhold Dieckbreder Brennkraftmaschine
DE1401980A1 (de) * 1959-02-16 1969-04-17 Wilhelm Buchmann Drehkolbenmaschine
DE4319896A1 (de) * 1993-01-09 1994-12-22 Klemm Gerhard Wilhelm Rotationskraft- und Arbeitsmaschine mit Druckausgleich

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1704254A (en) * 1926-05-15 1929-03-05 Jaffe John Motor
JPS54129211A (en) * 1978-03-30 1979-10-06 Hachirou Hayashida Disc engine
GB2104154A (en) * 1981-08-20 1983-03-02 Sebastiano Italia Rotary positive-displacement fluid-machines
DE3825365A1 (de) * 1988-07-26 1990-02-01 Armin Mylaeus Drehkolbenmaschine
DE29522008U1 (de) * 1995-01-19 1999-07-29 Raab, Anton Gerhard, 80686 München Kraftmaschine

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2438859A (en) * 2006-06-05 2007-12-12 Juan Zak Toroidal fluid machine
GB2438859B (en) * 2006-06-05 2011-11-23 Juan Zak Rotary combustion engine, compressor, pump and motor
RU2675639C2 (ru) * 2017-02-14 2018-12-21 Евгений Михайлович Пузырёв Роторно-винтовая машина

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