WO2002084078A1 - Dispositif de moteur thermique a pistons rotatifs - Google Patents

Dispositif de moteur thermique a pistons rotatifs Download PDF

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Publication number
WO2002084078A1
WO2002084078A1 PCT/DE2001/001437 DE0101437W WO02084078A1 WO 2002084078 A1 WO2002084078 A1 WO 2002084078A1 DE 0101437 W DE0101437 W DE 0101437W WO 02084078 A1 WO02084078 A1 WO 02084078A1
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WO
WIPO (PCT)
Prior art keywords
rotary piston
piston
pistons
engine device
oval
Prior art date
Application number
PCT/DE2001/001437
Other languages
German (de)
English (en)
Inventor
Martin Sterk
Original Assignee
Martin Sterk
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 Martin Sterk filed Critical Martin Sterk
Priority to PCT/DE2001/001437 priority Critical patent/WO2002084078A1/fr
Publication of WO2002084078A1 publication Critical patent/WO2002084078A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
    • F02G1/00—Hot gas positive-displacement engine plants
    • F02G1/04—Hot gas positive-displacement engine plants of closed-cycle type
    • F02G1/043—Hot gas positive-displacement engine plants of closed-cycle type the engine being operated by expansion and contraction of a mass of working gas which is heated and cooled in one of a plurality of constantly communicating expansible chambers, e.g. Stirling cycle type engines
    • F02G1/044—Hot gas positive-displacement engine plants of closed-cycle type the engine being operated by expansion and contraction of a mass of working gas which is heated and cooled in one of a plurality of constantly communicating expansible chambers, e.g. Stirling cycle type engines having at least two working members, e.g. pistons, delivering power output
    • F02G1/0445—Engine plants with combined cycles, e.g. Vuilleumier
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
    • F02G1/00—Hot gas positive-displacement engine plants
    • F02G1/04—Hot gas positive-displacement engine plants of closed-cycle type
    • F02G1/043—Hot gas positive-displacement engine plants of closed-cycle type the engine being operated by expansion and contraction of a mass of working gas which is heated and cooled in one of a plurality of constantly communicating expansible chambers, e.g. Stirling cycle type engines
    • F02G1/044—Hot gas positive-displacement engine plants of closed-cycle type the engine being operated by expansion and contraction of a mass of working gas which is heated and cooled in one of a plurality of constantly communicating expansible chambers, e.g. Stirling cycle type engines having at least two working members, e.g. pistons, delivering power output

Definitions

  • the invention relates to a rotary piston heat engine device, composed of two units, each with two mutually movably mounted pistons, which are rotatably mounted in each cylinder, the axes of symmetry of the pistons and the cylinder being collinear, and the pistons being mounted such that they are mutually movable, a plurality of effective displacements being formed between each two radial interfaces of the two respective pistons, which execute an oscillating movement with respect to one another when the engine is operating, and at least one device is provided which causes the oscillating movement to have a circular movement of both Piston is superimposed, wherein a heating device, a heat storage device and a cooling device are provided in connection with a pipe system through which inlet slots and outlet slots of the displacements of the at least one cylinder of the units are interconnected.
  • Stirling engines are known in the prior art. These are heat engines in which at least one piston reciprocally supported in a cylinder is moved by gases, the temperature of which is changed cyclically via a heating device, a heat storage device and a cooling device.
  • a disadvantage of such engines is heat losses, which are due to the cyclical temperature changes of the gases in connection with the difficulty in sealing the gases, due to the high pressures prevailing in the engines.
  • the service life of such motors is also very limited due to the high load and the associated rapid wear of the motor components.
  • the efficiency of most previously known Stirling engines is also physically limited by the efficiency of the regenerator.
  • Rotary piston engines are also known in the prior art.
  • the best known examples of rotary piston engines are the so-called Wankel engines.
  • Wankel engines In these engines, a piston formed with a plurality of rounded surfaces is mounted in a cylinder, the inner wall of which is not circular, but has a plurality of concave recesses.
  • the combustion chambers of this engine are each formed between the rounded surfaces of the piston and corresponding recesses in the cylinder.
  • the disadvantage of the Wankel engine is above all its complicated assembly, which requires a high level of production.
  • Another problem is the sealing of the engine. Very much so Small leaks lead to a reduction in engine performance, an increase in the toxic proportions in the exhaust gases and an increased fuel and oil consumption.
  • a rotary piston engine the principle of which is used in the present invention, is known from DE 197 40 133.
  • This rotary piston engine has a cubic capacity or working space that is larger than that of the Wankel engine and has the advantage that its combustion chambers are easy to seal, easy to fill and empty, and the expansion energy of the combustion gases or working gases is to a large extent kinetic Energy is converted.
  • a rotary piston heat engine device of the type mentioned is disclosed in DE 198 14 742.
  • the known device has the disadvantage that if the temperature is applied unevenly from the outside to the two units of the rotary piston heat engine device, the respective units are heated or cooled to different extents, so that there is a phase shift in the timing of the respective units can. This then leads to tensions in the gearwheels of the respective units which mesh with a torque output device, which in turn results in unnecessary material wear and reduced smoothness of the motor device.
  • the object of the invention is to develop a rotary piston heat engine device of the type mentioned at the outset based on the principle of the Stirling engine so that it is one compared to the known device reduced material wear and increased smoothness and lifetime.
  • the fact that two coupled torque output devices are provided means that a device is created in which a torque compensation between the two units is made possible when the timing of the relevant two units is shifted.
  • the device according to the invention also has the important advantage over the prior art that an arbitrary rotation angle positioning of a respective piston of the units is made possible in a predetermined manner, so as to achieve an optimization of the efficiency or the performance of the motor device.
  • the coupling of the coupled torque output devices is designed as a coupling.
  • the coupling of the coupled torque output devices are designed as a differential. According to a further preferred embodiment of the invention it is provided that the coupling of the torque output devices coupled to one another takes place via a chain.
  • the coupling of the torque output devices coupled to one another takes place via gearwheels.
  • the coupling of the torque output devices coupled to one another takes place via a fixed shaft.
  • the respective gears of the two units can also act jointly on the gears of a torque output device if, for example, these are due to elastic, play-supporting mounting of the gears or due to the use of elastic, damping materials in the acting as coupling device Shaft is able to absorb smaller voltages.
  • the engine according to the invention has a simpler construction. No parts such as valves, camshafts or crankshafts are required to control the engine control. All essential components of the engine have easy-to-grind cylindrical surfaces and can be manufactured with high precision at low cost. Sealing the motor is also no problem. Almost absolute tightness can be achieved with conventional sealing elements. This makes it possible to significantly reduce manufacturing costs. Further advantages of the engine are its small dimensions, a particularly effective design of a regenerator, the gas flow and the possibilities for optimization through changes in stroke speed, and targeted process disturbances.
  • the motor according to the invention is a rotary piston motor which operates in a cyclic process and which can optionally be equipped with a plurality of work spaces.
  • 2 units consisting of piston, cylinder and cylinder end faces, are connected to one another by a control device.
  • two pistons each with two piston vanes, are provided in each unit of the engine according to the invention, four working spaces being formed between the respective interfaces of the total of four piston vanes of each unit, and four double operations being provided for one revolution of the working shaft.
  • different masses of the pistons are preferably compensated for by recesses and / or additional masses on the pistons and / or the gear wheels. This increases the smoothness of the engine and reduces the stress on the components.
  • the axis of one piston is designed as a solid rod and the axis of the other in each unit Piston formed as a hollow rod, the inside diameter of which is dimensioned such that the solid rod of the one piston is movably supported in its collinear orientation.
  • the device for causing a circular movement superimposed on the oscillating movement (approx. 60 °) of the pistons preferably has six oval gear wheels, the main axes of which are each arranged in pairs perpendicular to one another.
  • two oval gears standing perpendicular to each other are each assigned to a cylinder, and the two other oval gears standing perpendicular to each other are assigned to a working shaft for delivering the engine power.
  • the four oval gearwheels of the cylinders are each connected to corresponding oval gearwheels of the working shaft, which are arranged vertically on them.
  • the axis of one piston is connected to a first oval gear and the axis of the other piston is connected to a second oval gear, these oval gears being arranged collinearly one behind the other and the main axes of these oval gears being perpendicular to one another
  • the first and second oval gearwheels are preferably connected to one another via a third and fourth oval gearwheel, the third and fourth oval gearwheels being arranged collinearly one behind the other on one axis, the main axes of the third and fourth oval gearwheels being perpendicular to one another.
  • a plurality of inlet and outlet slots is preferably assigned to each unit.
  • the two cylinders of the engine according to the invention preferably have differently dimensioned and differently arranged cylinder wall sections between the respective inlet and outlet openings.
  • a cylinder wall which spans only a few angular degrees, is preferably provided between a first inlet slot of an inlet slot pair and a first adjacent outlet slot of an outlet slot pair, and a cylinder wall is provided between the same inlet slot of the inlet slot pair and another outlet slot of the pair of outlet slots 60 spanned angular degrees.
  • a cylinder wall is preferably provided between a first inlet slot of a pair of inlet slots and a first adjacent outlet slot of a pair of outlet slots, which spans approximately 30 degrees, and a cylinder wall is provided between the same inlet slot of the pair of inlet slots and another outlet slot of the pair of outlet slots , which also spans about 30 degrees.
  • the asymmetry between the inlet and outlet openings of the first cylinder and the second cylinder in the engine according to the invention causes the working gas to be transported from one cylinder to the other in the correct time. This process creates the engine's work output.
  • the respective angular position of the slots is preferably provided in such a way that it corresponds in each case to the position of the respective combustion chamber, which is formed by the respective interfaces of the relevant sections of the piston wings, so that the working spaces are filled or emptied in a timely manner.
  • the interfaces of the pistons are preferably also each formed in a straight line, the same distances being provided between adjacent parts of opposing interfaces of the pistons.
  • This vibration behavior is accompanied by the formation of the first and second oval gearwheels in such a way that the ratio of the length of the longitudinal axis to the length of the wide axis of each gearwheel is approximately 2: 1.
  • the ovality of the gears must be changed and the inlet and outlet slots must be adapted to the piston interfaces.
  • the first and second oval gearwheels are preferably connected to one another via a third and fourth oval gearwheel, which are arranged collinearly one behind the other and whose main axes are perpendicular to one another.
  • the interfaces of the pistons are preferably formed in a straight line such that the same distances are specified between adjacent parts of opposing interfaces of the pistons.
  • the respective angular position of the inlet openings is preferably provided such that it corresponds in each case to the position of the respective working space, which is formed by the respective interfaces of the relevant portions of the piston wings, so that the working chambers are filled in a correct manner in time.
  • the respective angular position of the outlet openings is preferably provided such that it corresponds in each case to the position of the respective working space, which is formed by the respective interfaces of the relevant sections of the piston wings, so that the working chambers are emptied in a correct manner.
  • the four pistons for example, which are movably supported relative to one another, are preferably rotatably supported in two different cylinders.
  • a bridging line between a hot line and a cold line of the motor according to the invention which can be activated or deactivated via a valve device.
  • a pipe connection between the displacements is designed as a two-circuit system.
  • the hot line and the cold line of the pipe system can be carried out separately in the motor according to the invention.
  • the engine according to the invention can have the construction scheme of a valve-controlled Stirling engine without additional components.
  • the working gas preferably always takes the same flow direction in a respective pipe section.
  • the motor according to the invention can be used as a heat pump with the supply of mechanical energy.
  • the motor according to the invention can also be used as a refrigeration machine with the supply of mechanical energy.
  • the motor according to the invention can also be used as a Vuilleumier machine.
  • Fig.l a preferred embodiment of the rotary piston heat engine device according to the invention in a first
  • FIG.la the embodiment of the rotary piston arm motor device according to the invention shown in Figure 1 in another working position, also in a cross-sectional view.
  • FIG. 2 shows the cylinder of the rotary piston heat engine device shown in FIG. 1 in a partially broken view obliquely from above;
  • 2a shows a first piston half of a cylinder of the rotary piston heat engine device shown in FIG. 1 in an oblique view from below;
  • 2b shows a second piston half of a cylinder of the rotary piston heat engine device shown in FIG. 1 in an oblique view from above;
  • Fig. 3 is a functional block diagram of the rotary piston heat engine device shown in Fig. 1; 4 shows a further preferred embodiment of the rotary piston heat engine according to the invention
  • FIG. 4a shows a further preferred embodiment of the rotary piston heat engine device according to the invention. in another working position, in a
  • Cross-sectional view; 5 shows the two cylinders of an inventive
  • Rotary piston heat engine device according to FIG. 1 or 5, in a cross-sectional view, from which the relative position of the piston shafts and
  • two pistons 1, 2 are rotatably mounted in a cylinder 3, the axes of symmetry 4, 5 of the piston 1, the piston 2 and the cylinder 3 being aligned collinearly.
  • the axis 6 of one piston 1 is designed as a solid rod 6, and the axis 7 of the other piston 2 is designed as a hollow rod, the clear diameter of which is dimensioned such that the solid rod 6 is rotatably mounted in the hollow rod 7.
  • the pistons 1, 2 each have interfaces 10, 20, the same distances being specified between adjacent parts of opposing interfaces 10, 20.
  • a plurality of effective displacements 8, 9, 11, 12 is formed between the respective interfaces 10, 20, which are delimited on the outside by the cylinder 3, and at the ends by the cover plates 30 and 31.
  • two pistons 1 ', 2' are in a cylinder 3 ' rotatably supported, the axes of symmetry 4 ', 5' of the piston 1 ', the piston 2' and the cylinder 3 'are collinear.
  • the axis 6 'of one piston 1' is designed as a solid rod 6 ', and the axis 7' of the other piston 2 'is designed as a hollow rod, the inside diameter of which is dimensioned such that the solid rod 6' is rotatable in the hollow rod 1 'is stored.
  • the pistons 1 ', 2' each have interfaces 10 ', 20', the same distances being specified between adjacent parts of opposing interfaces 10 ', 20'.
  • a plurality of effective displacements 8 ', 9', 11 ', 12' is formed between the respective interfaces 10 ', 20', which are delimited on the outside by the cylinder 3 'and at the ends by the cover plates 30 and 31'.
  • the two cylinders of the engine device according to the invention have differently dimensioned and differently arranged cylinder wall sections between the respective inlet and outlet openings.
  • a cylinder wall is provided between a first inlet slot of an inlet slot pair and a first adjacent outlet slot of an outlet slot pair, which spans only a few degrees, and between the same inlet slot of the inlet slot pair and another outlet slot of the outlet slot pair, a cylinder wall is provided, which approx. 60 degrees spanned.
  • a cylinder wall between a first inlet slot of a pair of inlet slots and a first adjacent outlet slot of a pair of outlet slots provided that spans only about 30 degrees, and between the same inlet slot of the pair of inlet slots and another outlet slot of the pair of outlet slots, a cylinder wall is provided, which also spans about 30 degrees.
  • the asymmetry between the intake and exhaust ports of the first cylinder and the second cylinder cause the working gas to be transported from one cylinder to the other in a timely manner in such a way that the engine is capable of delivering work.
  • a device 110 shown in FIG. 2 causes, in the rotary piston heat engine device 100 according to the invention, a circular movement to be superimposed on the oscillating movement of the pistons 1 and 2 and the pistons 1 'and 2'.
  • the device 110 has six oval gear wheels 101, 102, 103, 104, 101 'and 104', the main axes 111, 112, 113, 114, 111 'and 114' of which are each arranged in pairs perpendicular to one another.
  • the axis 7 of the other piston 2 is connected to a first oval gear wheel 101
  • the axis 6 of the one piston 1 is connected to a second oval gear wheel 104
  • these oval gear wheels 101, 104 being arranged collinearly one behind the other and the main axes 111, 114 of these oval gear wheels 101, 104 are arranged perpendicular to one another.
  • the first oval gear 101 and the second oval gear 104 are connected to one another via a third oval gear 102 and a fourth oval gear 103, the gears 102 and 103 being arranged collinearly one behind the other on an axis 105 are, the respective main axes 112, 113 of the gear wheels 102, 103 are arranged perpendicular to each other.
  • the axis 7 'of the other piston 2' is connected to a first oval gear wheel 101 ', and the axis 6' of the one piston 1 'is connected to a second oval gear wheel 104', these oval gear wheels 101 ' , 104 'are arranged collinearly one behind the other and the main axes 111', 114 'of these oval gear wheels 101', 104 'are arranged perpendicular to one another.
  • the first oval gear 101 'and the second oval gear 104' are connected to one another via a third oval gear 102 and a fourth oval gear 103, the gears 102 and 103 being arranged in a collinear manner one behind the other on an axis 105, the respective main axes 112 , 113 of the gear wheels 102, 103 are arranged perpendicular to one another.
  • gears 102 and 103 are operated by both units (cylinders 3, and 3 ').
  • the oval gear wheels 101 to 104 and 101 'and 104' have a ratio of 2/1 with respect to the length of their longitudinal axes to that of their transverse axes.
  • the different, changing local power transmission of the gears 101 rsp. 104 causes the oscillating movement of the pistons 1, 2 to be a
  • the working shaft 5 rotates at the average speed of the two pistons 1 and 2.
  • Wave 6 is the rotational energy of the motor per itself
  • Rotation four times changing angular velocity removable as is desirable for example for operating compressors.
  • FIG. 1 and la show an embodiment of the engine device according to the invention, in which two cylinders 3, 3 'with respective piston pairs 1, 2 and 1', 2 'via a corresponding pipe system 201, 201', 202, 202 ', 203, 203 'and 204, 204' are coupled to one another via a heater 300, a cooler 400 and a regenerator or heat exchanger 200.
  • the working gas emerging from the cylinder 3 reaches the pipe system 204, 204' of the cylinder 3 'via a heat exchanger 200, to which it emits its heat, via a cooler 400, on which it is further cooled.
  • a heat exchanger 200 to which it emits its heat
  • the now cooled working gas passes through the inlet openings 131, 131' of the cylinder 3 'into the gaps between the pistons 1' and 2 'in the vicinity of these inlet openings, these piston gaps being enlarged, and the gaps , which adjoin the piston surfaces of pistons 1 ', 2' located opposite each other, are reduced in size, so that the working gas located there is pressed out of cylinder 3 'into pipe system 201, 201' via outlet openings 141, 141 '.
  • this working gas flows further through the regenerator or heat exchanger 200, where it absorbs heat from that working gas which flows through the heat exchanger 200 from the pipe system 203, 203'.
  • the now heated working gas originating from the pipe system 201, 201 ' continues is heated. From there it flows into the pipe system 202, 202 ', from where the cycle repeats.
  • the working gas printed in the pipe 203 subsequently passes through the regenerator 200 and the cooler 400 into the pipe 204, which opens into the inlet opening 131 of the cylinder 3 ', and the working gas printed into the pipe 203' passes through the regenerator 200 'and the cooler 400 'into the pipe 204' which flows into the inlet opening 131 '.
  • the working gas entering the inlet opening 131 of the cylinder 3 ' has thus released part of its heat to the regenerator 200 and has subsequently been further cooled by the cooler 400, so that it is also present at the inlet opening 131 a temperature which is greatly reduced compared to tube 203.
  • the working gas present at the inlet opening 131 ' has released a large part of its heat to the regenerator 200' and has subsequently been further cooled by the cooler 400 ', so that it is strongly at the inlet opening 131' of the cylinder 3 'in relation to the pipe 203' cooled form is present.
  • Cold working gas thus passes via the inlet openings 131, 131 'of the cylinder 3' into the gaps between the pistons 1 'and 2' below these inlet openings, the gaps between these pistons being enlarged and each through the opposite piston surfaces 10 ', 20 'the piston 1', 2 'formed gaps, which are located below the outlet openings 141, 141' of the cylinder 3 ', are reduced.
  • the working gases contained therein are pressed into the pipe 201 or the pipe 201 'via the outlet openings 141, 141'.
  • the working gas in the tube 201 is first preheated by the regenerator 200 and then heated by the heater 300, from where it enters the tube 202.
  • the working gas in the tube 201 ' is preheated by the regenerator 200' and then heated by the heater 300 ', from where it enters the tube 202'. The cycle described above is then repeated.
  • the operating sequence takes place in an identical manner in the motor devices according to the invention shown in FIGS. 1 and 1a and FIGS. 4 and 4a.
  • the working gas in the pipe system and the cylinders passes through four changes of state, which are predetermined by corresponding working cycles of the pistons of the cylinders 3, 3 '.
  • the working gas is compressed in the respective spaces between the pistons 1, 2, 1 ', 2' of the cylinders 3, 3 'by mutually moving the respective pistons towards one another and thereby undergoes a polytropic (adiabatic) temperature increase.
  • the working gas heated in this way which has been printed into the pipe 201 via the outlet opening 141 of the cylinder 3 'or into the pipe 201' via the outlet opening 141 'of the cylinder 3', becomes from the regenerators 200 'or 200 and the heaters 300' or 300 further heated, whereby the pressure prevailing in the working gas is further increased.
  • the heater 300' there is therefore an overall maximum pressure of the working gas in the entire pipe system.
  • Working gas which is under high pressure, therefore enters the cylinder 3 through the inlet openings 130, 130 'and passes between corresponding gaps between the pistons 1, 2 and presses these pistons apart at high pressure.
  • the thermal energy of the working gas is in this working cycle of the engine according to the invention by pressing apart the spaces between the pistons 1, 2 of the cylinder 3 in Rotational energy of these pistons is converted.
  • the working gas cools down adiabatically in a third change of state.
  • the working gas so relaxed is pressed out of the cylinder 3 via the outlet openings 140, 140 'by compressing the corresponding gaps between the pistons 1, 2 due to an expansion of the gaps between these pistons following in the direction of rotation of the engine ,
  • the working gas then undergoes a fourth state change by being further cooled by the regenerators 200 and 200 'and the coolers 400 and 400' so that it is in a greatly cooled state in the pipes 204 and 204 '.
  • the working gas is reheated by compression.
  • the axes of the two cylinders are arranged such that they are an isosceles triangle with the axis of the work shaft, from which the engine power can be removed form, the angle between the cathets is approximately 135 ° and the angle of the hypotenuse to a cathete is approximately 22.5 °.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)

Abstract

L'invention concerne un dispositif de moteur thermique à pistons rotatifs (100) composé de deux unités comportant deux pistons (1, 2) logés de manière mobile l'un par rapport à l'autre, logés par ailleurs de manière rotative dans un cylindre respectivement (3). Les axes de symétrie (4, 5) des pistons (1, 2) et du cylindre (3) sont colinéaires, et les pistons (1, 2) sont logés de manière mobile l'un par rapport à l'autre. Une pluralité d'espaces de course actifs (8, 9, 11, 12) est conçue entre respectivement deux interfaces radiales (10, 20) des deux pistons respectifs (1, 2). Lesdits espaces de course décrivent un mouvement oscillant l'un par rapport à l'autre lorsque le moteur (100) fonctionne, et au moins un système (110) permet de superposer un mouvement circulaire au mouvement oscillant des deux pistons (1, 2). Le dispositif selon l'invention comporte par ailleurs, un système de chauffage, un système d'accumulation thermique, et un système de refroidissement reliés à un système tubulaire.
PCT/DE2001/001437 2001-04-12 2001-04-12 Dispositif de moteur thermique a pistons rotatifs WO2002084078A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PCT/DE2001/001437 WO2002084078A1 (fr) 2001-04-12 2001-04-12 Dispositif de moteur thermique a pistons rotatifs

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/DE2001/001437 WO2002084078A1 (fr) 2001-04-12 2001-04-12 Dispositif de moteur thermique a pistons rotatifs

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Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2005045197A1 (fr) * 2003-10-29 2005-05-19 Sl-Trade Marks Gmbh Dispositif a moteur thermique a pistons rotatifs
DE10350442A1 (de) * 2003-10-29 2005-06-16 Sl-Trade Marks Gmbh Kreiskolben-Wärmemotor-Vorrichtung
WO2006038825A1 (fr) * 2004-10-04 2006-04-13 Petrica Lucian Georgescu Moteur thermique rotatif
IT201900015770A1 (it) 2019-09-06 2021-03-06 Ivar Spa Nuovo ciclo combinato seol
IT201900015776A1 (it) 2019-09-06 2021-03-06 Ivar Spa Macchina termica configurata per realizzare cicli termici e metodo per realizzare cicli termici

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4687427A (en) * 1986-04-24 1987-08-18 Seybold Frederick W Rotary internal combustion engine with uniformly rotating pistons cooperating with reaction elements having a varying speed of rotation and oscillating motion
US4744736A (en) * 1985-09-09 1988-05-17 Stauffer John E Compound rotary internal combustion engine
DE19740133A1 (de) * 1997-09-12 1999-03-25 Martin Sterk Kreiskolbenmotor
DE19814742C1 (de) 1998-04-02 2000-01-05 Martin Sterk Kreiskolben-Wärmemotor-Vorrichtung

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4744736A (en) * 1985-09-09 1988-05-17 Stauffer John E Compound rotary internal combustion engine
US4687427A (en) * 1986-04-24 1987-08-18 Seybold Frederick W Rotary internal combustion engine with uniformly rotating pistons cooperating with reaction elements having a varying speed of rotation and oscillating motion
DE19740133A1 (de) * 1997-09-12 1999-03-25 Martin Sterk Kreiskolbenmotor
DE19814742C1 (de) 1998-04-02 2000-01-05 Martin Sterk Kreiskolben-Wärmemotor-Vorrichtung

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2005045197A1 (fr) * 2003-10-29 2005-05-19 Sl-Trade Marks Gmbh Dispositif a moteur thermique a pistons rotatifs
DE10350442A1 (de) * 2003-10-29 2005-06-16 Sl-Trade Marks Gmbh Kreiskolben-Wärmemotor-Vorrichtung
DE10350442B4 (de) * 2003-10-29 2007-11-29 Sl-Trade Marks Gmbh Kreiskolben-Wärmemotor-Vorrichtung
US7328579B2 (en) 2003-10-29 2008-02-12 Sl Trade Marks Gmbh Rotary piston heat engine system
WO2006038825A1 (fr) * 2004-10-04 2006-04-13 Petrica Lucian Georgescu Moteur thermique rotatif
IT201900015770A1 (it) 2019-09-06 2021-03-06 Ivar Spa Nuovo ciclo combinato seol
IT201900015776A1 (it) 2019-09-06 2021-03-06 Ivar Spa Macchina termica configurata per realizzare cicli termici e metodo per realizzare cicli termici

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