EP3144471B1 - 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
EP3144471B1
EP3144471B1 EP15186100.2A EP15186100A EP3144471B1 EP 3144471 B1 EP3144471 B1 EP 3144471B1 EP 15186100 A EP15186100 A EP 15186100A EP 3144471 B1 EP3144471 B1 EP 3144471B1
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EP
European Patent Office
Prior art keywords
sealing strips
rotary
fluid
rotary piston
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.)
Not-in-force
Application number
EP15186100.2A
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German (de)
English (en)
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EP3144471A1 (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 PCT/EP2016/071937 priority patent/WO2017050648A1/fr
Priority to US15/761,213 priority patent/US10458238B2/en
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 from exhaust energy
    • F01N5/04—Exhaust or silencing apparatus combined or associated with devices profiting from 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 14.
  • 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.
  • DE 10 2007 019 958 A1 describes a rotary engine with two rotary pistons.
  • the two rotary pistons comprise on their outer side in each case a sprocket, which is in each case interrupted by two recesses and two working teeth.
  • the recesses and working teeth have the same, semi-circular shape and contact each other by sealing.
  • sealing strips are provided, which are pressed by a spring to the outside and so press against the housing inner wall sealing.
  • GB 576 603 A relates to a rotary engine with also two rotary pistons, each comprising two protruding bulges and appropriately shaped recesses. The bulges sealingly contact the recesses and the housing inner wall.
  • sealing strips can be arranged in the bulges, which are pressed by springs sealing against the housing inner wall.
  • Other rotary piston engines with two rotary pistons, which each have three bulges and correspondingly shaped depressions, so that the bulges of one of the rotary pistons engage sealingly in the depressions of the other rotary piston, are described in: DE 44 39 063 A1 .
  • DE 26 35 972 A1 and FR 698 019 A are described in: DE 44 39 063 A1 .
  • DE 26 35 972 A1 and FR 698 019 A
  • 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 depressions 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, whereby the radial direction is 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.
  • 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 are pressed / deformed by the fluid sealing against the housing inner wall.
  • 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 arranged in the interior, that the fluid can only pass from the inlet opening to the outlet opening, when the rotary pistons are rotated. In other words, 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 In order to produce a deformation for the sealing contacting of the housing inner wall, the fluid contact side has no convex shape or at least on its inner wall facing the end of the end no convex shape. Rather, the fluid contact side has a concave shape or at least at its the housing inner wall end facing a concave shape .
  • 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, in particular through the concave fluid contact side or when 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, thereby causing a rotation of the rotary piston.
  • 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 that is generated by the rotary engine to produce rotational energy is being used.
  • rather moderate amounts of energy are to be used.
  • 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 may differ from the number described for 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 should be a seal to each other and a seal to the surrounding housing inner wall Provide 12 so that the fluid can not reach the outlet opening 15 at standstill of the rotary piston 20, 30.
  • 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 are made 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 generates a rotational movement from the energy of the fluid.
  • 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)

Claims (14)

  1. Moteur à pistons rotatifs
    - avec un boîtier (10), lequel forme un espace interne (11),
    - avec deux pistons rotatifs (20, 30), lesquels sont agencés dans l'espace interne (11),
    - avec une ouverture d'entrée (13) pour conduire un fluide dans l'espace interne (11) et
    - avec une ouverture de sortie (15) pour le fluide, laquelle se situe dans l'espace interne (11), sur un côté situé en face de l'ouverture d'entrée (13),
    - tandis que chaque piston rotatif (20, 30) présente, sur son pourtour externe, au moins deux baguettes d'étanchéité (25, 26, 35, 36) et au moins deux creux (27, 28, 37, 38),
    - tandis que les baguettes d'étanchéité (25, 26, 35, 36) sont dimensionnées, dans une direction radiale, de sorte à être en contact étanche avec une paroi interne du boîtier (12),
    - tandis que les baguettes d'étanchéité (25, 26, 35, 36) sont formées dans un matériau déformable,
    - tandis que chacune des baguettes d'étanchéité (25, 26, 35, 36) présente, pour une position d'angle de rotation du piston rotatif correspondant (20, 30), pour laquelle cette baguette d'étanchéité (25, 26, 35, 36) est en contact avec la paroi interne du boîtier (12), un côté de contact de fluide (35A), lequel est orienté vers un fluide affluant,
    caractérisé en ce que
    - les formes des creux (27, 28, 37, 38) et des baguettes d'étanchéité (25, 26, 35, 36) sont choisies pour que les baguettes d'étanchéité (25, 26, 35, 36) d'un des pistons rotatifs respectif (20, 30) s'engagent de manière étanche dans les creux (27, 28, 37, 38) de l'autre piston rotatif respectif (20, 30), et
    - le côté de contact de fluide (35A) de chaque baguette d'étanchéité (25, 26, 35, 36) a une forme concave.
  2. Moteur à pistons rotatifs selon la revendication 1
    caractérisé en ce que
    une zone d'extrémité de chaque côté de contact de fluide (35A) a une forme concave.
  3. Moteur à pistons rotatifs selon la revendication 1 ou 2
    caractérisé en ce que
    chacune des baguettes d'étanchéité (25, 26, 35, 36) présente une face arrière (35B), laquelle est située en face du côté de contact de fluide (35A), et, pour une position d'angle de rotation du piston rotatif correspondant (20, 30), pour laquelle cette baguette d'étanchéité (25, 26, 35, 36) est en contact avec la paroi interne du boîtier (12), n'est pas orientée vers du fluide affluant, et
    la face arrière (35B) a une forme convexe.
  4. Moteur à pistons rotatifs selon les revendications 1 à 3
    caractérisé en ce que
    les pistons rotatifs (20, 30) présentent, sur leurs pourtours extérieurs respectifs, des rainures pour recevoir et maintenir les baguettes d'étanchéité (25, 26, 35, 36) et
    les baguettes d'étanchéité (25, 26, 35, 36) sont formées en tant qu'écrous pour rainures pour s'engager fixement dans les rainures du piston rotatif respectif (20, 30).
  5. Moteur à pistons rotatifs selon la revendication 4
    caractérisé en ce que
    les rainures sont formées en tant que rainures en forme de T et chacun des écrous pour rainures présente un col (35C) latéralement saillant pour s'engager dans l'une des rainures en forme de T.
  6. Moteur à pistons rotatifs selon une des revendications 1 à 5
    caractérisé en ce que
    chaque piston rotatif (20, 30) comprend, sur son pourtour externe, exactement deux joints d'étanchéité (25, 26, 35, 36) à des positions d'angle opposées et chaque piston rotatif (20, 30) comprend exactement deux creux (27, 28, 37, 38), lesquels sont situés sur le pourtour externe à des positions d'angles, qui sont respectivement décalées de 90° par rapport aux positions d'angle des deux joints d'étanchéité (25, 26, 35, 36).
  7. Moteur à pistons rotatifs selon une des revendications 1 à 6,
    caractérisé en ce que
    les joints d'étanchéité (25, 26, 35, 36) sont dimensionnés et une paroi interne du boîtier (12) est formée de telle sorte que les joints d'étanchéité (25, 26, 35, 36), au sein d'une zone d'angle de rotation des pistons rotatifs (20, 30), sont en contact étanche avec la paroi interne du boîtier (12).
  8. Moteur à pistons rotatifs selon une des revendications 1 à 7
    caractérisé en ce que
    chacun des pistons rotatifs (20, 30) présente, sur son pourtour externe, une couronne dentée (23, 33) et
    les pistons rotatifs (20, 30) sont agencés de telle sorte que leurs couronnes dentées (23, 33) s'imbriquent les unes dans les autres.
  9. Moteur à pistons rotatifs selon la revendication 8
    caractérisé en ce que
    les joints d'étanchéité (25, 26, 35, 36), dans une direction radiale par rapport à leur piston rotatif respectif (20, 30), font saillie plus loin vers l'extérieur que la couronne dentée respective (23, 33).
  10. Moteur à pistons rotatifs selon la revendication 8 ou 9
    caractérisé en ce que
    les joints d'étanchéité (25, 26, 35, 36) font saillie au-dessus de la couronne dentée respective (23, 33) d'une distance radiale comprise entre 5 % et 30 %, et plus particulièrement entre 10 % et 25 %, d'un radius de la couronne dentée (23, 33).
  11. Système de récupération de chaleur résiduelle
    avec un circuit de fluide de travail, dans lequel un fluide est mis en circulation, avec un échangeur thermique grâce auquel de la chaleur d'un milieu peut être transférée au fluide dans le circuit de fluide de travail,
    tandis que le circuit de fluide de travail est configuré en tant que cycle, en particulier en tant que cycle de Rankine organique, et présente des moyens pour la transformation d'énergie thermique du fluide en énergie de mouvement, caractérisé en ce que
    le cycle de fluide de travail comprend un moteur à pistons rotatifs selon une des revendications 1 à 10, dans lequel du fluide affluant se détend et, ainsi, une rotation des pistons rotatifs (20, 30) est déclenchée.
  12. Système de récupération de chaleur résiduelle selon la revendication 11
    caractérisé en ce que
    un générateur est disponible et agencé de sorte à ce qu'il transforme de l'énergie de rotation du moteur à pistons rotatifs en énergie électrique.
  13. Véhicule avec un système de récupération de la chaleur résiduelle selon la revendication 11 ou 12
    caractérisé en ce que
    l'échangeur thermique est agencé de telle sorte que la chaleur de gaz d'échappement peut être transférée au fluide.
  14. Procédé pour le fonctionnement d'un moteur à pistons rotatifs
    - pour lequel un fluide est conduit, par une ouverture d'entrée (13), dans un espace interne (11) d'un boîtier (10) du moteur à pistons rotatifs,
    - pour lequel, dans l'espace interne (11), sont agencés deux pistons rotatifs (20, 30), lesquels sont mis en rotation par le fluide,
    - tandis que chaque piston rotatif (20, 30) présente, sur son pourtour extérieur, au moins deux joints d'étanchéité (25, 26, 35, 36) et au moins deux creux (27, 28, 37, 38),
    - tandis que les joints d'étanchéité (25, 26, 35, 36) sont dimensionnés, dans une direction radiale, de sorte à être en contact étanche avec une paroi interne du boîtier (12),
    - tandis que les joints d'étanchéité (25, 26, 35, 36) sont composés d'un matériau déformable,
    - tandis que chacun des joints d'étanchéité (25, 26, 35, 36) présente, pour une position d'angle de rotation du piston rotatif correspondant (20, 30), pour laquelle cette baguette d'étanchéité (25, 26, 35, 36) est en contact avec la paroi interne du boîtier (12), un côté de contact de fluide (35A), lequel est orienté vers un fluide affluant,
    caractérisé en ce que
    - les formes des creux (27, 28, 37, 38) et des baguettes d'étanchéité (25, 26, 35, 36) sont choisies pour que les baguettes d'étanchéité (25, 26, 35, 36) d'un des pistons rotatifs respectif (20, 30) s'engagent de manière étanche dans les creux (27, 28, 37, 38) de l'autre piston rotatif respectif (20, 30),
    - le fluide venant de l'ouverture d'entrée (13) fait pression contre certains des joints d'étanchéité (25, 26, 35, 36), ce qui presse ces joints d'étanchéité (25, 26, 35, 36) contre la paroi interne du boîtier (12), et
    - le côté de contact de fluide (35A) de chaque baguette d'étanchéité (25, 26, 35, 36) a une forme concave.
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
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
US15/761,213 US10458238B2 (en) 2015-09-21 2016-09-16 Rotary piston engine and method for operating a rotary piston engine
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 EP3144471A1 (fr) 2017-03-22
EP3144471B1 true EP3144471B1 (fr) 2018-02-28

Family

ID=54196814

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Application Number Title Priority Date Filing Date
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

Country Status (4)

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

Families Citing this family (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
EP3628816A1 (fr) * 2018-09-25 2020-04-01 Fuelsave GmbH Moteur à combustion interne à liaison fonctionnelle réglable de ses unités motrices

Family Cites Families (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1426820A (en) * 1921-01-12 1922-08-22 Spokane Irrigation Pump Compan Rotary pump
FR698019A (fr) * 1930-02-25 1931-01-26 Pompe rotative
GB576603A (en) * 1944-03-22 1946-04-11 Richard Rutherford Improvements in and relating to rotary machines, such as motors, compressors, pumps and the like
US2604051A (en) * 1945-12-14 1952-07-22 Keelavite Co Ltd Rotary pump
DE2635972A1 (de) * 1976-08-10 1978-02-16 Borsig Gmbh Aussenachsige drehkolbenmaschine
US4646693A (en) * 1983-04-18 1987-03-03 Zachary Fayngersh Rotary engine
DE4324749A1 (de) * 1993-07-23 1995-01-26 Freudenberg Carl Fa Regelventil
DE4439063A1 (de) * 1994-11-02 1995-06-14 Anton Prim Rotationskolbenmotor mit besonders angeordneten Abgasöffnungen, Abgasnutzung, Absaugen der Restabgase, Antrieb durch Explosionsgase, Wasserdampf oder comprimierte Luft
US8215935B2 (en) * 2000-05-12 2012-07-10 Gyroton Corporation Multiple rotor fluid transfer engine
DE10339857A1 (de) * 2003-08-29 2005-03-24 Daimlerchrysler Ag Brennkraftmaschine mit einer Motorbremseinrichtung
JP4544106B2 (ja) * 2005-09-08 2010-09-15 マツダ株式会社 エンジンの過給装置
DE102007019958B4 (de) * 2006-08-14 2011-11-10 Ralf Hettrich Vielzahndrehkolbenmotor mit extrem hohen Drehmoment bei niedrigsten als auch bei sehr hohen Drehzahlen wie in Bereichen einer Turbine, als Antrieb oder zum Einsatz der Energiegewinnung, Energieumwandlung oder Energierückgewinnung
US8181624B2 (en) * 2006-09-05 2012-05-22 Terry Michael Van Blaricom Open-cycle internal combustion engine
GB0717212D0 (en) * 2007-09-05 2007-10-17 Cummins Turbo Tech Ltd Multi-stage turbocharger system
GB2475534B (en) * 2009-11-21 2014-11-12 Cummins Turbo Tech Ltd Sequential two-stage turbocharger system
US9435203B2 (en) * 2010-10-22 2016-09-06 Peter South Rotary positive displacement machine
GB201307610D0 (en) * 2013-04-26 2013-06-12 Controlled Power Technologies Ltd Exhaust Driven Turbine-Generator Integrated Gas Energy Recovery System

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

Also Published As

Publication number Publication date
US20180258768A1 (en) 2018-09-13
EP3144471A1 (fr) 2017-03-22
ZA201801910B (en) 2018-11-28
WO2017050648A1 (fr) 2017-03-30
US10458238B2 (en) 2019-10-29

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