EP3144471A1 - Moteur a piston rotatif et procede d'entrainement d'un moteur a piston rotatif - Google Patents

Moteur a piston rotatif et procede d'entrainement d'un moteur a piston rotatif Download PDF

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Publication number
EP3144471A1
EP3144471A1 EP15186100.2A EP15186100A EP3144471A1 EP 3144471 A1 EP3144471 A1 EP 3144471A1 EP 15186100 A EP15186100 A EP 15186100A EP 3144471 A1 EP3144471 A1 EP 3144471A1
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EP
European Patent Office
Prior art keywords
rotary piston
sealing strips
fluid
rotary
sealing
Prior art date
Legal status (The legal status 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 status listed.)
Granted
Application number
EP15186100.2A
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German (de)
English (en)
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EP3144471B1 (fr
Inventor
Dirk Hoffmann
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Fuelsave GmbH
Original Assignee
Fuelsave GmbH
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 Fuelsave GmbH filed Critical Fuelsave GmbH
Priority to EP15186100.2A priority Critical patent/EP3144471B1/fr
Priority to US15/761,213 priority patent/US10458238B2/en
Priority to PCT/EP2016/071937 priority patent/WO2017050648A1/fr
Publication of EP3144471A1 publication Critical patent/EP3144471A1/fr
Application granted granted Critical
Publication of EP3144471B1 publication Critical patent/EP3144471B1/fr
Priority to ZA2018/01910A priority patent/ZA201801910B/en
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • F01C1/00—Rotary-piston machines or engines
    • F01C1/08—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing
    • F01C1/12—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of other than internal-axis type
    • F01C1/123—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of other than internal-axis type with tooth-like elements, extending generally radially from the rotor body cooperating with recesses in the other rotor, e.g. one tooth
    • 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
    • F01C19/00—Sealing arrangements in rotary-piston machines or engines
    • F01C19/02—Radially-movable sealings for working fluids
    • F01C19/06—Radially-movable sealings for working fluids of resilient material
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL-COMBUSTION ENGINES
    • F01N5/00—Exhaust or silencing apparatus combined or associated with devices profiting by exhaust energy
    • F01N5/04—Exhaust or silencing apparatus combined or associated with devices profiting by exhaust energy the devices using kinetic energy

Definitions

  • the present invention relates in a first aspect to a rotary engine according to the preamble of claim 1.
  • the invention relates to a method for operating a rotary piston engine according to the preamble of claim 15.
  • a rotary engine is used to convert energy into rotational energy.
  • the rotary piston engine is set in motion by the pressure of a fluid.
  • the fluid can be basically arbitrary and the pressure can arise in basically any arbitrary manner.
  • a generic rotary piston engine has for this purpose a housing which forms an interior. In the interior, at least two rotary pistons are arranged. In addition, an inlet opening for introducing a fluid into the interior space is provided, and an outlet opening for the fluid is provided, which is located on the interior at an opposite side of the inlet opening. The fluid thus flows through the interior and thereby puts the rotary pistons in rotation.
  • a fluid is passed through an inlet opening into an interior of a housing of the rotary piston engine.
  • a fluid is passed through an inlet opening into an interior of a housing of the rotary piston engine.
  • at least two rotary pistons are arranged, which are set in rotation by the fluid.
  • an object of the invention can be considered to provide a rotary piston engine and a method for operating a rotary piston engine, wherein the rotary piston engine offers the highest possible efficiency for the widest possible range of applications.
  • each rotary piston has at least two sealing strips and at least two recesses on its outer circumference.
  • the shapes of the recesses and the sealing strips are selected to, in particular sealing, engagement of the sealing strips of each one of the rotary piston in the recesses of the other rotary piston.
  • the sealing strips are dimensioned in the radial direction for sealingly contacting a housing inner wall.
  • each rotary piston has at least two sealing strips and at least two recesses on its outer circumference, wherein the shapes of the recesses and the sealing strips are selected for, in particular sealing, engagement of the sealing strips of one each the rotary piston in the wells of the other rotary piston.
  • the sealing strips are dimensioned in the radial direction for sealingly contacting a housing inner wall.
  • the radial direction refers to the radius of the associated rotary piston, thus the radial direction transverse or perpendicular to the direction of rotation of the respective rotary piston.
  • the fluid coming from the inlet orifice presses against (at least) some of the sealing strips, whereby these sealing strips are pressed against the housing inner wall.
  • at least one (or exactly one) of the sealing strips of each rotary piston can be exposed to the inflowing fluid and thus be pressed by this against the inner wall of the housing.
  • sealing strips which are on or attached to the rotary piston.
  • a fluid pressure can act on the sealing strips and press them against the housing inner wall, whereby a particularly good seal is produced.
  • the fluid pressure leads to a certain deformation of the sealing strips, which is important for an efficient seal.
  • the sealing fluid pressure can already be achieved at a relatively low pressure. Also, the viscosity of the working fluid plays only a minor role. Therefore, the rotary engine of the invention can be used for many different working fluids and under very different pressures. As a further advantage, lubricants or oils are not required in the rotary piston engine according to the invention, depending on the fluid used.
  • sealing strips comprise a deformable or elastic material, so that they can be pressed / deformed in a sealing manner against the housing inner wall by the fluid.
  • the material of the sealing strips is easier to deform or more elastic than a material surrounding the sealing strips of the rotary piston, in particular as the material from which the grooves described in more detail below for receiving the sealing strips are formed.
  • the fluid used may in principle be any liquid or gas. This is passed through the inlet opening into the interior of the rotary piston engine. As it flows through the interior in the direction of the outlet opening, it rotates the two rotary pistons.
  • the rotary pistons are dimensioned and in the Interior space arranged that the fluid can only pass from the inlet opening to the outlet opening, when the rotary pistons are rotated.
  • the two rotary pistons cause a seal at standstill, so that no fluid can flow through the interior without rotation.
  • a contact of the two rotary pistons is necessary. Through this contact little or no fluid can pass between the two rotary pistons.
  • a contact of the two rotary pistons to the housing inner wall is required for the seal.
  • each rotary piston by means of its sealing strips provide a sealing contact with the adjacent housing inner wall over an angular range of at least 150 °, preferably at least 180 ° and more preferably more than 180 °.
  • the sealing strips may extend in a longitudinal direction, which is substantially parallel to the axes of rotation of the two rotary pistons.
  • an angle between the longitudinal direction and the axes of rotation may be less than 20 °, preferably less than 10 °.
  • the two axes of rotation of the two rotary pistons can also be parallel to each other or at least at an angle which is at most 40 ° or preferably at most 20 °.
  • the two rotary pistons can be formed identically. If asymmetrical sealing strips are used, as described later, then the rotary pistons can be identical except for a mirrored arrangement or shaping of the sealing strips.
  • an object Under a rotary piston, an object can be understood, which is rotatably mounted and rotates with rotation, a shaft. The rotation of this shaft can then be used, for example, to set other objects in rotation or in particular to generate electrical energy via a generator.
  • the sealing strips can be received in grooves, ie grooves or similar recesses, which are formed on the respective outer circumference of the rotary piston.
  • the grooves can be formed in later described in more detail sprockets of the rotary piston.
  • the sealing strips can be attached in principle any way. The sealing strips can thus be exchangeable, so that when worn due to the sealing contact a slight change of the sealing strips is possible without further components of the rotary piston engine would have to be replaced.
  • the sealing strips are formed as sliding blocks for retaining engagement in the grooves in the rotary piston.
  • the sealing strips have at their respective inner end, which is accommodated in the associated rotary piston, a thickening or a collar.
  • the grooves in which the sealing strips are received, are shaped so that said thickening or the collar engages holding.
  • the grooves may be formed as T-grooves and each of the sliding blocks may include a laterally projecting collar for engaging one of the T-slots.
  • the grooves therefore have a T-shape in a section transverse or perpendicular to the axis of rotation of the associated rotary piston.
  • a the inside of the rotary piston facing the end of Nuteinsteine also has a T-shape, so that the sliding block is held in the T-slot.
  • screw fasteners or adhesive connections can be provided for fastening the sealing strips in the grooves.
  • the sealing strips and the associated grooves can be shaped so that the sealing strips are held in the radial direction of the associated rotary piston, so are immovable.
  • moving perpendicularly thereto, in particular in the direction of the axis of rotation of the rotary piston can be possible (and thus insertion and removal) of the sealing strips.
  • worn or abraded sealing strips can be easily replaced.
  • the sealing effect of the sealing strips to the housing inner wall depends on the deformation of the sealing strips. It is advantageous if the fluid pressure causes a deformation of the sealing strips toward the housing inner wall, and not about a deformation away from the housing inner wall.
  • Each of the sealing strips has a side which, in the case of a rotational angle position of the associated rotary piston, in which the sealing strip contacts the housing inner wall, faces inflowing fluid. This page will be referred to hereinafter as the fluid contact side.
  • the fluid contact side preferably has no convex shape or at least on its inside facing the housing inner end no convex shape. Rather, the fluid contact side may rather have a concave shape or at least have a concave shape at its end facing the inner wall of the housing. Alternatively, a substantially planar course of the fluid contact side can also provide sufficient deformation depending on the circumstances.
  • Each of the sealing strips also has a rear side, which faces the fluid contact side. This rear side is not facing inflowing fluid when there is a rotational angle position of the associated rotary piston in which the sealing strip contacts the housing inner wall or is adjacent thereto.
  • the shape of the back also affects the deformation and thus the sealing effect.
  • the rear side is preferably not concave or at least not concave on one end facing the inside wall of the housing.
  • the rear side is convexly shaped or at least convexly formed on an end facing the inner wall of the housing. A sufficient sealing effect can in turn be possible even with a linear or planar shape of the back.
  • the sealing strips may have an edge, at which a sealing contact with the housing inner wall is effected.
  • An edge may result from a non-circular cross-section, especially if the fluid contact side is concave and the back is convex.
  • each rotary piston has (in particular exactly) two sealing strips at opposite angular positions on its outer circumference.
  • the two angular positions can be offset by a rotation angle of 180 ° about the axis of rotation of the associated rotary piston to each other.
  • each rotary piston may comprise two recesses, which are located on the outer circumference at angular positions, which are also offset by 180 ° to each other and preferably each offset by 90 ° to the angular positions of the two sealing strips. This ensures that inflowing fluid always presses against one of the sealing strips on each rotary piston and thereby causes a rotation of the rotary piston.
  • this arrangement ensures that regardless of a current Rotary position of the rotary piston is always provided a seal of both rotary pistons to the housing inner wall.
  • the sealing strips can be sized and a housing inner wall to be shaped so that the sealing strips within a rotational angle range of the rotary piston, the housing inner wall sealingly contact.
  • This rotation angle range can be located opposite to a contact area between the two rotary pistons.
  • the molding of the housing inner wall is such that over a rotational angle range, which may be, for example, between 5 ° and 20 °, two sealing strips contact the housing inner wall and otherwise contacted only a sealing strip the housing inner wall.
  • Each of the rotary pistons may have a ring gear on its outer periphery.
  • the rotary pistons can then be arranged so that their sprockets interlock. This largely prevents fluid from flowing between the two rotary pistons. Rather, the fluid is transported at the edge between the rotary piston and the housing inner wall.
  • the sprockets may be interrupted by the depressions and sealing strips and extend, moreover, over the entire circumference of the two rotary pistons. Under a sprocket can be understood that an outer peripheral surface of the associated rotary piston has radially projecting teeth. Preferably, each tooth extends over the entire height of the rotary pistons along their axes of rotation.
  • the sealing strips can protrude in the radial direction of their respective rotary piston further outward than the respective sprocket.
  • the ring gear is always spaced from the housing inner wall. In between, a free space is formed, via which fluid passes in the direction of the outlet opening. The free space is limited in the circumferential direction of the rotary piston by the sealing strips.
  • the sealing strips protrude over the respective sprocket preferably by a radial distance, which is between 5% and 30%, in particular between 10% and 25%, of a radius of the sprocket. This radius can be measured from the center of the rotary piston to the outer periphery of the associated ring gear.
  • the protruding radial distance influences the size of a deformation of the sealing performance and thus influences the sealing properties.
  • the protruding radial distance is decisive for the amount of fluid that is conveyed past the associated rotary piston. It has been shown that with the aforementioned values, a good seal can be achieved and a high efficiency can be achieved over a relatively large range of flow rates.
  • a radial size of teeth of the sprockets is preferably at most 15%, preferably at most 10%, of a radius of the sprocket.
  • the radius of the ring gear may be defined by the distance from its center to its outer periphery, so the outer end of the teeth.
  • the rotary piston engine can serve any purpose in which energy from a fluid pressure to be used.
  • thermal energy can be utilized by transferring it to the fluid and ultimately contributing to the fluid pressure utilized by the rotary engine to generate rotational energy.
  • applications come into consideration which are rather moderate amounts of energy to use.
  • An example is the use of heat energy from exhaust gases of an internal combustion engine, such as vehicles.
  • the invention also relates to a waste heat recovery system having a working fluid circuit in which the fluid is circulated.
  • heat can be transferred from a medium to the fluid in the working fluid circuit by means of a heat exchanger.
  • the named medium can basically be arbitrary.
  • it may be exhaust gases of an internal combustion engine, in particular an internal combustion engine of a vehicle.
  • the working fluid circuit is designed as a cyclic process and includes means for converting thermal energy of the fluid into kinetic energy. Such cycle processes are known in principle.
  • the working fluid circuit can be designed as an organic Rankine cycle (ORC, Organic Rankine Cyle) and comprise the components required for this purpose.
  • ORC Organic Rankine Cyle
  • an inventive rotary piston engine As an essential feature is provided as an engine of the cycle (or instead of the turbine used in such cycles), an inventive rotary piston engine. In this, the fluid flowing through is expanded and thus a rotation of the rotary piston is effected.
  • ORC process other cycles can be used in which a motor is driven by thermal energy.
  • the cyclic process may include, for example, a feed pump, a heater or the heat exchanger, the rotary piston engine according to the invention and a condenser and optionally a recuperator.
  • the invention further relates to a vehicle, such as a car or truck with an internal combustion engine, wherein the vehicle has the waste heat recovery system according to the invention.
  • the heat exchanger can be arranged so that exhaust gas heat can be transferred to the fluid.
  • an exhaust pipe may adjoin the heat exchanger so as to transfer heat from the exhaust pipe.
  • the heat exchanger already suffices if, for example, an exhaust gas line is in thermal contact with a line of the fluid.
  • the rotary engine is described with two rotary pistons. In principle, however, other rotary pistons may also be present in the same interior or in another interior. In addition, the number of sealing strips and associated recesses differ from the number described in the various embodiments.
  • Fig. 1 is shown schematically a cross section of an embodiment of a rotary piston engine 100 according to the invention. An enlarged section of this is in Fig. 2 shown.
  • the rotary engine 100 is driven by a fluid flowing through and serves to convert energy of the fluid into rotational energy.
  • the rotary piston engine 100 comprises as essential components two rotary pistons 20 and 30, which are arranged in an inner space 11. This is limited by a housing inner wall 12 of a housing 10.
  • An inlet opening 13, not shown, allows a fluid to flow into the interior 11.
  • the fluid may in principle be any liquid or any gas or liquid-gas mixture.
  • an outlet opening 15 for the fluid is also present. If the fluid flows from the inlet opening 13 through the interior 11 to the outlet opening 15, it must pass through the two rotary pistons 20, 30 for this purpose and causes them to rotate. With the reference numerals 21 and 31, the axes of rotation of the two rotary pistons 20 and 30 are indicated. The axes of rotation 21, 31 extend into the plane of the drawing.
  • the design of the rotary pistons 20, 30 is crucial. These are to provide a seal to one another and a seal to the surrounding housing inner wall 12, so that the fluid can not reach the outlet opening 15 when the rotary pistons 20, 30 are at a standstill.
  • the rotary pistons 20, 30 should be easily drivable by the fluid, that is to say rotate even at low pressure.
  • the two rotary pistons 20 and 30 have at their respective outer sides via sealing strips 25, 26, 35, 36.
  • the outer sides can be regarded as lateral surfaces of approximately cylindrical rotary pistons 20, 30.
  • the sealing strips 25, 26, 35, 36 preferably extend over the entire height of the inner space 11, wherein the height can extend in the direction of the axes of rotation 21, 31.
  • the rotary piston 20 has at least two, preferably exactly two, sealing strips 25, 26. Likewise, at least two, preferably exactly two, sealing strips 35, 36 are arranged on the rotary piston 30. The sealing strips 25, 26, 35, 36 project radially beyond the remaining outer circumference of the associated rotary piston 20, 30.
  • the sealing strips 25, 26, 35, 36 are preferably received in grooves on the respective rotary piston 20, 30 and may preferably consist of a different material than the part of the rotary piston 20, 30, in which the grooves are formed.
  • the sealing strips 25, 26, 35, 36 may consist of a deformable material. This may be, for example, rubber, resin or a plastic. As a result, the sealing strips 25, 26, 35, 36 can be slightly deformed by countercurrent fluid and pressed against the housing inner wall 12.
  • the sealing strips 25, 26, 35, 36 but also consist of a rigid material, such as metal.
  • the sealing strips 25, 26, 35, 36 may be accommodated with some freedom in their associated grooves, whereby the fluid pressure, the sealing strips 25, 26, 35, 36 can easily tilt.
  • the sealing strips 25, 26, 35, 36 are also pressed sealingly against the housing inner wall 12.
  • the two rotary pistons 20, 30 are arranged in the interior 11 so that they touch each other. As a result, a fluid flow between the rotary piston is largely excluded.
  • the rotation axes 21 and 31 may be parallel to each other. But it is also an inclination between the axes of rotation 21, 31 possible, as long as a largely sealing contact between the rotary piston 20, 30 is ensured.
  • the rotary pistons 20, 30 at their respective outer circumference also each have a toothed rim 23, 33, which is rigidly connected to the remaining part of the associated rotary piston 20, 30.
  • the two sprockets 23, 33 are sized and arranged so that they mesh. As a result, both sprockets 23, 33 rotate together and form hardly any voids between each other. Fluid can therefore hardly pass between the two sprockets 23, 33.
  • the rotary pistons 20 and 30 at their respective outer periphery recesses 27, 28 and 37, 38.
  • the number of recesses 27, 28 of the first rotary piston 20 is equal to the number of sealing strips 35, 36 of the second rotary piston 30 is selected.
  • the number of recesses 37, 38 of the second rotary piston 30 is equal to the number of sealing strips 25, 26 of the first rotary piston 20 is selected.
  • the sealing strips 35, 36 of the second rotary piston 30 meet straight on the recesses 27, 28 of the first rotary piston 20.
  • a recess and a sealing strip alternate.
  • the two sealing strips 25, 26 at an azimuth angle of 180 ° (ie, a 180 ° angle about the axis of rotation 21 around) spaced from each other.
  • the two recesses 27, 28 are also offset by an azimuth angle of 180 ° to each other and additionally offset in each case by an azimuth angle of 90 ° to the sealing strips 25, 26.
  • a rotation angle is relevant, via the same sealing strip 25, 26 35, 36 causes a seal to the housing inner wall 12.
  • This rotation angle can, as in Fig. 1 may be greater than 180 ° and, for example, between 185 ° and 240 °.
  • the housing wall 12 at each of the rotary pistons has a circular section shape, wherein this shape forms a circular section of greater than 180 °, that forms more than a semicircle.
  • sealing strips 25, 26 35, 36 are closer in Fig. 2 recognizable.
  • the sealing strip 35 is shown there in its cross section.
  • the sealing strip 35 may be shaped like a profile, that is over its length (in particular in the direction of the axis of rotation 31) have the same cross-sectional shape.
  • the cross-sectional shape forms a sliding block.
  • a collar 35C is formed toward the inner end of the sealing strip 35. This engages in a T-shaped depression / groove. This prevents that the sliding block can unintentionally come loose in the radial direction from the groove of the rotary piston.
  • Inserting and removing the sliding block 35 is possible in the longitudinal direction, that is to say in the direction of the axis of rotation 31. Due to the formation as sliding blocks, the sealing strips are on the one hand easy to attach. On the other hand, replacement is also simplified. This is significant because it may come to a gradual abrasion of the sealing strips 25, 26, 35, 36 due to the sealing contact with the housing inner wall 12 and so an exchange may be required.
  • a sealing strip 35 is shown, which protrudes radially from the toothed rim 33.
  • the sealing strip 35 has a point of maximum radial extent, or an edge extending into the plane of the drawing (or extending in the direction of the axis of rotation 31). From this edge, the sealing strip 35 has a surface 35A or fluid contact side 35A, which faces the inflowing fluid (this applies to rotational positions in which the sealing strip 35, the housing inner wall 12 contacted).
  • the sealing strip 35 On the other side of said edge, the sealing strip 35 has another surface 35B, which is also referred to as the back 35B. The back side 35B does not face the inflowing fluid when the sealing strip 35 contacts the housing inner wall 12.
  • the fluid contact side 35A has a recess or a concave shape, while the back side 35B has an outwardly curved or convex shape.
  • the outer end of the sealing strip 35 ie the radially outermost part, is deformed transversely or approximately perpendicularly to the radial direction by the countercurrent fluid.
  • the sealing strip 35 is pressed against the housing inner wall 12.
  • Fig. 2 the lower end of the sealing strip 35 is deformed approximately to the left and thus against the housing inner wall 12.
  • a particularly good seal can be produced thereby, but without generating an unduly high friction between the sealing strips and the housing inner wall.
  • the rotary pistons can therefore advantageously be set in rotation.
  • low pressure fluids can also be used for energy usage.
  • an internal combustion engine emits exhaust gases from a vehicle, the heat of which can be used in principle.
  • the heat can be transferred with a heat exchanger to a fluid in a working cycle.
  • the working cycle according to the principle of the generally known Rankine cycle or organic Rankine cycle (ORC, English: Organic Rankine Cycle)
  • ORC Organic Rankine Cycle
  • the working fluid is compressed and relaxed again. It passes through a motor, which from the energy of the fluid a rotational movement generated.
  • the rotary piston engine according to the invention is used.
  • the waste heat utilization of exhaust gases pressures are generated in which previously used engines have a rather poor efficiency.
  • the rotary piston engine according to the invention makes it possible to efficiently utilize heat energy from exhaust gases.
  • the generated rotational energy can be used in principle any way. In particular, it can be converted into electrical energy, such as with a generator.
  • the electrical energy can be fed into an electrical system of the motor vehicle and / or stored in an electrochemical battery or other storage means.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Hydraulic Motors (AREA)
EP15186100.2A 2015-09-21 2015-09-21 Moteur a piston rotatif et procede d'entrainement d'un moteur a piston rotatif Not-in-force EP3144471B1 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
EP15186100.2A EP3144471B1 (fr) 2015-09-21 2015-09-21 Moteur a piston rotatif et procede d'entrainement d'un moteur a piston rotatif
US15/761,213 US10458238B2 (en) 2015-09-21 2016-09-16 Rotary piston engine and method for operating a rotary piston engine
PCT/EP2016/071937 WO2017050648A1 (fr) 2015-09-21 2016-09-16 Moteur à pistons rotatifs et procédé de fonctionnement d'un moteur à pistons rotatifs
ZA2018/01910A ZA201801910B (en) 2015-09-21 2018-03-22 Rotary piston engine and method for operating a rotary piston engine

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP15186100.2A EP3144471B1 (fr) 2015-09-21 2015-09-21 Moteur a piston rotatif et procede d'entrainement d'un moteur a piston rotatif

Publications (2)

Publication Number Publication Date
EP3144471A1 true EP3144471A1 (fr) 2017-03-22
EP3144471B1 EP3144471B1 (fr) 2018-02-28

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EP15186100.2A Not-in-force EP3144471B1 (fr) 2015-09-21 2015-09-21 Moteur a piston rotatif et procede d'entrainement d'un moteur a piston rotatif

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Country Link
US (1) US10458238B2 (fr)
EP (1) EP3144471B1 (fr)
WO (1) WO2017050648A1 (fr)
ZA (1) ZA201801910B (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3527781A1 (fr) 2018-02-14 2019-08-21 Fuelsave GmbH Moteur à piston rotatif et procédé d'entraînement d'un moteur à piston rotatif
US11255258B2 (en) * 2018-09-25 2022-02-22 Fuelsave Gmbh Internal combustion engine having adjustable linking of its engine units

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EP3527781A1 (fr) 2018-02-14 2019-08-21 Fuelsave GmbH Moteur à piston rotatif et procédé d'entraînement d'un moteur à piston rotatif
WO2019158449A1 (fr) 2018-02-14 2019-08-22 Fuelsave Gmbh Moteur à pistons rotatifs et procédé pour faire fonctionner un moteur à pistons rotatifs
CN111954749A (zh) * 2018-02-14 2020-11-17 燃料节省有限公司 旋转活塞发动机和用于操作旋转活塞发动机的方法
US11098587B2 (en) * 2018-02-14 2021-08-24 Fuelsave Gmbh Rotary piston engine and method for operating a rotary piston engine
CN111954749B (zh) * 2018-02-14 2022-04-01 燃料节省有限公司 旋转活塞发动机和用于操作旋转活塞发动机的方法
US11255258B2 (en) * 2018-09-25 2022-02-22 Fuelsave Gmbh Internal combustion engine having adjustable linking of its engine units

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US20180258768A1 (en) 2018-09-13
US10458238B2 (en) 2019-10-29
ZA201801910B (en) 2018-11-28
EP3144471B1 (fr) 2018-02-28

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