EP3214262B1 - Unité moteur-compresseur - Google Patents

Unité moteur-compresseur Download PDF

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Publication number
EP3214262B1
EP3214262B1 EP17158650.6A EP17158650A EP3214262B1 EP 3214262 B1 EP3214262 B1 EP 3214262B1 EP 17158650 A EP17158650 A EP 17158650A EP 3214262 B1 EP3214262 B1 EP 3214262B1
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EP
European Patent Office
Prior art keywords
compressor
engine
rotary
axis
motor
Prior art date
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Application number
EP17158650.6A
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German (de)
English (en)
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EP3214262A3 (fr
EP3214262A2 (fr
Inventor
Detlev Kils-Korte
Rudolf Schulze
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Individual
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Individual
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Publication of EP3214262A2 publication Critical patent/EP3214262A2/fr
Publication of EP3214262A3 publication Critical patent/EP3214262A3/fr
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B35/00—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for
    • F04B35/002—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for driven by internal combustion engines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B13/00—Reciprocating-piston machines or engines with rotating cylinders in order to obtain the reciprocating-piston motion
    • F01B13/04—Reciprocating-piston machines or engines with rotating cylinders in order to obtain the reciprocating-piston motion with more than one cylinder
    • F01B13/06—Reciprocating-piston machines or engines with rotating cylinders in order to obtain the reciprocating-piston motion with more than one cylinder in star arrangement
    • F01B13/068—Reciprocating-piston machines or engines with rotating cylinders in order to obtain the reciprocating-piston motion with more than one cylinder in star arrangement the connection of the pistons with an actuated or actuating element being at the inner ends of the cylinders
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B57/00—Internal-combustion aspects of rotary engines in which the combusted gases displace one or more reciprocating pistons
    • F02B57/08—Engines with star-shaped cylinder arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B63/00—Adaptations of engines for driving pumps, hand-held tools or electric generators; Portable combinations of engines with engine-driven devices
    • F02B63/06—Adaptations of engines for driving pumps, hand-held tools or electric generators; Portable combinations of engines with engine-driven devices for pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/04—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B27/0404—Details, component parts specially adapted for such pumps
    • F04B27/0409—Pistons
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/04—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B27/0404—Details, component parts specially adapted for such pumps
    • F04B27/0423—Cylinders
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/04—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B27/047—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement with an actuating element at the outer ends of the cylinders
    • F04B27/0472—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement with an actuating element at the outer ends of the cylinders with cam-actuated distribution members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/04—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B27/053—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement with an actuating element at the inner ends of the cylinders
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/04—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B27/06—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement the cylinders being movable, e.g. rotary
    • F04B27/065—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement the cylinders being movable, e.g. rotary having cylinders in star- or fan-arrangement, the connection of the pistons with an actuating element being at the inner ends of the cylinders
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/04—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B27/06—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement the cylinders being movable, e.g. rotary
    • F04B27/065—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement the cylinders being movable, e.g. rotary having cylinders in star- or fan-arrangement, the connection of the pistons with an actuating element being at the inner ends of the cylinders
    • F04B27/0657—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement the cylinders being movable, e.g. rotary having cylinders in star- or fan-arrangement, the connection of the pistons with an actuating element being at the inner ends of the cylinders rotary cylinder block
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B35/00—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for
    • F04B35/06—Mobile combinations

Definitions

  • the present invention relates to a motor-compressor unit according to the preamble of claim 1, which comprises a rotary motor and a rotary compressor.
  • the rotary motor and the rotary compressor are coupled to one another in such a way that the rotary compressor can be driven by the rotary motor.
  • torque is transmitted between the rotary motor and the rotary compressor.
  • the motor-compressor unit can have an input/output shaft that is connected to both the rotary motor and the rotary compressor.
  • the distance between the piston axis and the engine axis is also referred to as eccentricity.
  • the up and down movement of the engine pistons within the associated cylinders is due to the fact that the engine pistons and the engine rim each rotate about different axes of rotation, namely the engine rim around the engine axis and the engine pistons around the piston axis. Both the engine rim and the engine pistons each rotate on a circular path during operation of the rotary engine.
  • Units that include both a drive, in particular a motor, and a compressor are already known in the prior art.
  • a drive in particular a motor
  • a compressor for example, on the US Patent Application 2007/0172363 A1 referred.
  • This includes a motor-compressor unit in which an unspecified drive interacts with an axial compressor.
  • the motor-compressor unit is characterized in that it is arranged in a common housing.
  • the well-known motor-compressor unit is shielded from the environment by means of this housing.
  • the document mentioned deals with a special routing of the air compressed by means of the compressor, with at least a proportion of the compressed air being used to cool the drive.
  • a rotary engine of the type described above also results from the U.S. Patent 1,968,694 .
  • This patent shows a rotary engine having an engine ring with a plurality of cylinders and a corresponding number of engine pistons, the engine pistons being each articulated by connecting rods to a common connecting rod disc.
  • the connecting rod disk rotates about a piston axis, which is offset by an eccentricity to the engine axis of the rotary engine shown.
  • the control of the valves of the individual cylinders is particularly complicated.
  • a rotary engine which discloses an engine housing with a cam track, with which the valves of the cylinders are controlled.
  • the present invention is based on the object of providing a motor-compressor unit that can be operated in particular without a supply of electrical power, with the simplest possible rotary motor advantageously being used.
  • the rotary motor comprises a motor housing with at least one motor rim rotatably mounted in the motor housing.
  • the motor rim is rotatably mounted about a motor axis of the motor housing.
  • At least one cylinder preferably a plurality of cylinders, is arranged within the motor rim, with a motor piston being arranged in each of the cylinders.
  • An engine piston delimits a combustion chamber together with the wall of the respectively associated cylinder, the engine piston being guided inside the cylinder so as to be linearly movable along a central axis of the respective cylinder. In other words, the volume of the combustion chamber can be changed by moving the engine piston along the cylinder axis.
  • the motor piston or pistons are each guided by connecting rods, with the motor pistons being mounted so as to be rotatable overall about a piston axis.
  • the motor piston or pistons are rotated in such a way that the motor pistons revolve on a circular path around the piston axis.
  • the piston axis is oriented parallel to and spaced from the engine axis. In other words, is the piston axis arranged eccentrically to the motor axis. The consequence of this is that the motor rim and the motor pistons rotate about different axes or revolve on different circular paths.
  • the engine pistons perform the described up and down movement within their cylinders of the engine rim.
  • the rotary compressor comprises a compressor housing with at least one compressor ring which is mounted rotatably in the compressor housing and is mounted such that it can rotate about a compressor axis of the compressor housing.
  • the compressor ring comprises at least one cylinder, with a compressor piston being arranged in the cylinder. Together with a wall of the cylinder, this delimits a compressor chamber, with the compressor piston being guided in a linearly movable manner in the cylinder of the compressor ring.
  • the compressor piston is at least indirectly connected to a piston axis of the rotary compressor by means of a connecting rod, so that the compressor piston rotates on a circular path around the piston axis when the rotary compressor is in operation.
  • the piston axis is arranged parallel to the compressor axis and offset by an eccentricity at a distance from the compressor axis. While the compressor ring rotates about the compressor axis and the compressor piston—as described—rotates about the piston axis, during the operation of the rotary compressor, analogous to the rotary engine described above, a continuous relative movement takes place between the compressor pistons and the respectively associated cylinder, as a result of which an up and down Ab-movement of the compressor pistons in the cylinders is due.
  • the rotary motor and the rotary compressor are coupled to one another in a torque-transmitting manner by means of a transmission device, with the motor housing and the compression housing each having a radially inwardly extending elevation over a partial angular range on their inner lateral surfaces, with the at least one cylinder of the rotary motor and the at least one Cylinders of the rotary compressor each have at least one valve device, by means of which media can be discharged from the combustion chamber of the rotary motor or compressed gas from the compressor chamber of the rotary compressor during operation of the motor-compressor unit, and the valve device at least over a partial angular range of a complete revolution of the Cylinder about the motor axis engages away with the motor housing, wherein at least one valve element of the valve device can be forced out of its sealing seat by means of the engagement, so that a flow ungstechnische connection between the combustion chamber of the cylinder and an environment can be released or released and at least one turbo pipe by means of which a fluidic connection between a gas outlet opening of the
  • this coupling of rotary motor and rotary compressor takes place in such a way that a speed of the rotary motor is transmitted directly to the rotary compressor, so that the latter consequently rotates around the compressor axis at the same speed.
  • the transmission device has a gear that allows a different rotation of the rotary motor and the rotary compressor.
  • a speed ratio between rotary motor and rotary compressor can be adjusted.
  • the motor-compressor unit according to the invention offers the particular advantage that it can be operated independently of electricity.
  • the rotary engine is particularly suitable for burning suitable fuels and driving the rotary compressor in this way.
  • the rotary engine acts to convert chemical energy into mechanical energy.
  • the rotary compressor can consequently be operated by means of the coupling of the rotary motor to the rotary compressor and the merger that takes place in this way to form the motor-compressor unit.
  • all suitable substances can be considered as fuels for the rotary engine, in particular natural gas, petrol or diesel.
  • the combination of a compressor with an internal combustion engine offers the advantage that the compressor can be operated independently of an electrical power supply. This can be particularly beneficial in regions that are not supplied with electricity.
  • the rotary engine is advantageously operated as a two-stroke engine. This means that each of the pistons performs two strokes within the cylinder between two consecutive ignitions in the associated cylinder. This type of operation of the rotary engine is particularly simple compared to four-stroke operation and contributes to increased longevity of the rotary engine.
  • the rotary motor and the rotary compressor are each mounted in an associated housing, the rotary motor in a motor housing and the rotary compressor in a compressor housing.
  • an elevation extends on an inner lateral surface of the respective housing over a partial angular range relative to the motor axis or the compressor axis.
  • This Elevation is such that a high point of the elevation measured from the respective axis of rotation of the respective rotary machine has a smaller radial distance than the other points of the respective housing outside of this elevation. This geometric relationship is explained below with reference to the exemplary embodiment.
  • a corresponding motor housing with an elevation offers the particular advantage that it can be used for mechanical control of a valve device of a cylinder of the rotary engine.
  • valve control can be carried out particularly easily by means of two mechanical forces, namely the centrifugal force that occurs due to the rotation of the rotary motor and the other by means of an axial force that is transmitted by means of a transmission element.
  • the transmission element is suitable for transmitting an axial force, which is directed in the radial direction of the rotary engine, to an associated valve disk or another valve element of the motor rim, for example.
  • valve device together with a corresponding valve plate is pressed into its sealing seat due to the acting centrifugal force, so that the combustion chamber of a respective cylinder is sealed off from its surroundings.
  • the valve device In the area of the elevation on the inner lateral surface of the motor housing, however, the valve device is forced to move relative to the motor rim when viewed in the radial direction relative to the motor axis, in that a transmission element, which interacts with the elevation, moves due to the form fit between the valve device and the Survey must move in the radial direction in which extends the survey viewed in the radial direction.
  • valve train To design the valve train, a designer is now free to provide one or more bumps along the perimeter of the motor housing and determine their arc length relative to the motor axis. In this way, depending on individual application alone by changing a positioning of a survey and the geometry of the valve control of the associated rotary motor can be adjusted freely.
  • valve control is correspondingly particularly robust and is also possible independently of an electrical supply, for example a complex control or the like.
  • the centrifugal control described does not require such aids. It may only be necessary for a start-up phase of the rotary motor to provide a corresponding valve spring, since there may not yet be sufficient centrifugal forces acting on the valve device. However, such a valve spring remains inoperative in an operating phase of the rotary engine.
  • an associated valve device includes a guide element, in particular a roller or a carriage, by means of which the valve device is guided on the inner lateral surface of the motor housing.
  • the inner lateral surface preferably has a corresponding guide element, for example in the form of a guide groove or a guide rail.
  • the valve device is reliably guided along a constant trajectory of the motor housing and guided over the elevation with each revolution, as a result of which the valve is opened cyclically and then closed again due to the centrifugal forces acting.
  • the guide element of the motor housing must be designed accordingly so that the guide element of the motor rim is guided over the elevation only during every second revolution, thus causing the respective valve to open.
  • the same has at least one turbo pipe, by means of which a fluidic connection between a gas outlet opening of the rotary compressor and a gas inlet opening of the rotary motor can be established or established.
  • a turbo pipe can be used for a compressed gas starting from a respective cylinder of the rotary compressor to a corresponding cylinder of the rotary engine.
  • the rotary compressor acts at least partially, preferably completely, as a turbocharger for the rotary engine. Supercharging the rotary engine is suitable for increasing its efficiency.
  • the cylinders of the rotary motor and the rotary compressor are assigned to each other, being arranged relative to the transmission axis with only a small angular offset of a maximum of 20°, preferably a maximum of 10°, more preferably completely offset.
  • the cylinders of the rotary motor and the rotary compressor are advantageously arranged one behind the other in alignment or slightly twisted relative to one another, viewed along an axis of the motor-compressor unit.
  • such a turbo pipe can be designed completely straight, that is to say it can be designed without kinks, curves or other deflections over its longitudinal axis.
  • both the rotary engine and the rotary compressor are operated at the same speed, so that the turbo pipe or pipes can be firmly connected to the cylinders assigned to them.
  • the rotary engine and the rotary compressor are advantageously each equipped with the same number of cylinders.
  • a cylinder of the rotary compressor is preferably assigned to each of the cylinders of the rotary engine, with each pair of cylinders being fluidically coupled by means of a turbo pipe.
  • turbo pipe is continuously cooled by its rotation together with the rotary motor and the rotary compressor.
  • a temperature problem as often occurs in the prior art with known turbochargers, can be avoided in this way.
  • the straight, i.e. non-bent, design of the turbo pipe also contributes to this.
  • the valve device is positively engaged with the motor housing at least over a partial angular range of a complete revolution of the cylinder around the engine axis, wherein at least one valve element of the valve device can be lifted out of its sealing seat by means of the engagement, so that a fluidic connection between the combustion chamber of the cylinder and a Environment is releasable or released.
  • the rotary motor and the rotary compressor of the motor-compressor unit according to the invention are advantageously arranged along a common axis, with the motor axis of the rotary motor and the compressor axis of the rotary compressor coinciding.
  • This common axis of the motor-compressor unit also forms a transmission axis of the transmission device, by means of which the rotary motor and the rotary compressor are connected to one another.
  • the arrangement of the rotary motor and the rotary compressor directly next to each other or one above the other is particularly advantageous with regard to the torque-resistant coupling of the two rotary machines, since only a rigid connection between the motor ring and the compressor ring has to be created.
  • the rotary motor and/or the rotary compressor are mounted by means of a stationary crankshaft.
  • the rotary motor and the rotary compressor are advantageously mounted on a common, stationary crankshaft.
  • the crankshaft or a shaft axis thereof is arranged in such a way that the motor rim or the compressor rim rotates around it.
  • the shaft axis of the crankshaft advantageously coincides with the engine axis or the compressor axis. It follows from this that the piston axes of the rotary engine or rotary compressor must be spaced apart from the shaft axis of the crankshaft around the eccentric point.
  • the crankshaft has at least one offset, this offset containing the respective piston axis.
  • the crankshaft is only made up of individual plates and pins that can be assembled without any special technical effort.
  • the crankshaft has plates whose diameter exceeds the diameter of the actual shaft, pins being arranged parallel to the shaft axis in a radially outer area of these plates.
  • the engine pistons of the rotary engine or the compressor pistons of the rotary compressor can then move around this fixed eccentricity rotate around the pins of the crankshaft, which creates the eccentric rotation between the engine ring and the compressor ring and their respective pistons.
  • the motor-compressor unit would comprise a total of three essential axes of rotation, namely the shaft axis of the crankshaft, which also contains the motor axis of the rotary engine and the compressor axis of the rotary compressor, the piston axis of the rotary engine and the piston axis of the rotary compressor. These axes are each arranged parallel to one another and at a distance from one another.
  • the elevation of the motor housing and the elevation of the compressor housing offset relative to the transmission axis of the motor-compressor unit, in particular to arrange them opposite one another.
  • the elevation serves to open a valve or the associated valve device. If a rotary engine is coupled to a rotary compressor, there is the possibility of using the rotary compressor to supercharge the rotary engine, that is to say as a turbocharger, so to speak. For this it is necessary that the valves of the rotary engine and the rotary compressor open at different points in time on their orbit around the transmission axis.
  • the valving of the rotary engine opens to discharge exhaust gas from the respective associated cylinders, while the opening of the valves of the rotary compressor serves to discharge the compressed gas from the respective cylinder. If this compressed gas is intended for introduction into the combustion chamber of a respective cylinder of the rotary engine, it will be understood that the valving of the rotary engine should be closed at the time of introduction of the compressed gas, while the valving of the rotary compressor must be open. A described offset of the elevations is therefore particularly advantageous in such a case.
  • the described opposite of the elevations viewed relative to the transmission axis of the motor-compressor unit is particularly advantageous when the motor-compressor unit or at least the rotary motor thereof is operated in two-stroke operation.
  • the rotary motor and the rotary compressor are combined in a common motor-compressor housing.
  • a motor-compressor housing includes both the motor housing of the rotary motor and the compressor housing of the rotary compressor.
  • a motor-compressor unit designed in this way forms a uniform component, with the motor-compressor housing preferably having a uniform diameter and thus having a constant outside diameter viewed along its longitudinal axis. It is particularly advantageous for this if the motor rim of the rotary motor and the compressor rim of the rotary compressor have at least essentially, preferably completely, identical dimensions.
  • both the rotary engine and the rotary compressor each have the same number of cylinders, which preferably also correspond to one another, i.e. viewed relative to the transmission axis or motor axis or compressor axis without offset are aligned to each other.
  • a corresponding embodiment results, for example, from the exemplary embodiment below.
  • Such a generator unit is suitable for converting kinetic energy into electrical energy, with the generator unit comprising at least one generator housing in which a rotor is mounted so as to be rotatable about a generator shaft.
  • This generator shaft must be able to be coupled to the transmission device at least temporarily in a force-transmitting manner, so that an output torque of the rotary motor can be transmitted to the generator unit.
  • a generator unit it is advantageous to arrange the rotary motor "between" the rotary compressor and the generator unit, with the axes of rotation of the rotary motor, the rotary compressor and the generator unit advantageously being identical.
  • the generator housing when a generator unit is provided, it can be advantageous to construct the generator housing as part of a common housing, to a certain extent an overall housing.
  • the motor-compressor unit as such and the generator unit are assembled in a common housing and form a structural unit.
  • the mechanical implementation of a valve control by means of an elevation described above is particularly easy to achieve by means of a guide groove or a guide rail, with the guide groove or the guide rail being arranged circumferentially and closed on the inner lateral surface of the motor housing and/or the compressor housing and, to a certain extent, via the Survey leads away, that is, interacts with the respectively assigned survey.
  • the valve device can be guided in this guide groove or on the guide rail. In this way, with each revolution of the rotary motor, the valve means is forced to engage the boss and cause the valve to open.
  • valve device interacts with a roller or a guide carriage, by means of which the valve device can interact with the described guide groove or the described guide rail.
  • the embodiment in the Figures 1 to 7 comprises a motor-compressor unit 1 according to the invention, which is formed by a rotary motor 2 according to the invention and a rotary compressor 3 .
  • the rotary motor 2 and the rotary compressor 3 are power-transmittingly coupled to each other by means of a transmission device 10 .
  • this transmission device 10 consists of a coupling structure formed by a plurality of rods oriented parallel to a transmission axis 9 of the motor-compressor unit 1 .
  • the rotary motor 2 and the rotary compressor 3 are constructed essentially the same.
  • the rotary engine 2 has an engine ring 4, which includes a total of six cylinders 6 in the example shown here.
  • a motor piston 7 is mounted in a linearly movable manner.
  • a motor piston 7 and a respectively associated cylinder 6 or its outer wall jointly define a combustion chamber 26 in which a fuel, for example gas or petrol, is burned during operation of the rotary motor 2 .
  • the individual engine pistons 7 are each connected in a force-transmitting manner to a connecting rod disk 34 by means of a connecting rod 8 .
  • a respective connecting rod 8 is coupled to the respectively associated engine piston 7 by means of a piston joint 30 .
  • each of the connecting rod disks 34 is also connected to a master connecting rod 32 .
  • the master connecting rod 32 is connected torque-proof to the connecting rod disk 34 ; the master connecting rod 32 is also not connected in an articulated manner to the associated engine piston 7 , so that rotation of the engine piston 7 relative to the master connecting rod 32 is blocked.
  • the present rotary engine 2 has a total of six cylinders 6 and consequently equally six engine pistons 7 and six connecting rods 8, 32. All connecting rods 8 of the rotary engine 2 are coupled to the same connecting rod disk 34 .
  • the individual connecting rods 8 lie in one plane and are not arranged offset relative to one another when viewed along the motor axis 5 .
  • the master connecting rod 32 is articulated in a torque-proof manner at a center point of the connecting rod disk 34 .
  • This center point of the connecting rod disk 34 lies on a piston axis 11 of the rotary engine 2.
  • This piston axis 11 describes the axis around which the engine pistons 7 revolve as the engine rim 4 rotates.
  • An associated circular path 40 is particularly popular figure 1 recognizable.
  • the piston axis 11 is oriented parallel to the motor axis 5 of the rotary motor 2 and is offset from the motor axis 5 by an eccentricity 41 .
  • this eccentricity 41 between the engine axis 5 and the piston axis 11 causes a linear stroke movement of the engine pistons 7 within the cylinder 6 to be converted into a rotary movement of the engine rim 4 .
  • This principle is already known under the name "rotary motor”.
  • the individual connecting rods 8 are not aligned parallel to a connecting axis of the piston axis 11 and the respective piston joint 30 of the respectively associated engine piston 7 , but are pivoted with respect to this connecting axis. This applies to all connecting rods 8 with the exception of the master connecting rod 32; the latter is directly coupled to the piston axis 11 in a straight line. This arrangement is necessary in order to reduce the degree of rotation of the connecting rod disk 34 from the value 2 to the value 1 and thereby to force the movement of the individual engine pistons 7 onto the circular path 40 provided for them.
  • the rotary compressor 3 is in principle identical to the rotary motor 2 .
  • Compressor pistons 15 are guided in a linearly movable manner within the cylinder 14 of the rotary compressor 3 .
  • the compressor pistons 15 are each attached in turn by means of a connecting rod 16 to a connecting rod disk 34 , which is a separate connecting rod disk.
  • the connecting rods 8 of the rotary motor 2 and the connecting rods 16 of the Rotary compressor 3 arranged on different connecting rod disks 34 .
  • the rotary compressor also has a master connecting rod 32 .
  • the rotary engine 2 shown here is operated as a two-stroke engine, with the associated engine piston 7 within the cylinder 6 performing two strokes during a full revolution of a cylinder 6 of the rotary engine 2 by 360° around the engine axis 5 .
  • position of the rotary engine 2 is the right cylinder 6 in an ignition position in which the engine piston 7 is in an upper reverse position.
  • the combustion chamber 26 of the cylinder 6 has its minimum volume.
  • the motor piston 7 is rotated once completely about the piston axis 11 and is thereby moved from its upper reversing position to its lower reversing position and back again.
  • the lower reversing position of a motor piston 7 is at the in figure 1 Cylinder 6 shown on the left can be observed.
  • the two-stroke operation of the rotary engine 2 results in one ignition taking place in each of the cylinders 6 for each revolution of the engine rim 4 . It is basically irrelevant whether this ignition takes place by means of a spark plug (e.g. petrol engine) or independently (e.g. diesel engine).
  • a spark plug e.g. petrol engine
  • independently e.g. diesel engine
  • loading can take place particularly easily by means of a gas inlet opening 25 , of which each of the cylinders 6 has one.
  • the gas inlet openings 25 are arranged on the cylinders 6 in such a way that they are only released when the respective engine piston 7 is in its lower reversing position.
  • This position of a respective engine piston 7 is particularly advantageous for filling the combustion chamber 26 since, following the lower reversal position, the engine piston 7 moves back towards its upper reversal position and in the course of this the volume of the combustion chamber 26 is continuously reduced.
  • This reduction in the volume of the combustion chamber 26 results in compression of the gas in the combustion chamber and consequently a significant increase in pressure within the combustion chamber 26. This favors combustion conditions for the next ignition when the engine piston 7 is in its top reversal position.
  • the motor-compressor unit 1 has a special feature in the example shown.
  • both the rotary motor 2 and the Rotary compressor 3 are each equipped with the same number of cylinders 6, 14 .
  • these cylinders 6, 14 are arranged in pairs. This means that each of the cylinders 6 of the rotary motor 2 corresponds to a cylinder 14 of the rotary compressor 3 in such a way that they have no angular offset relative to the motor axis 5 or the compressor axis 13 or the transmission axis 9 .
  • the individual cylinders 6, 14 are arranged one behind the other or aligned, viewed along the transmission axis 9 of the motor-compressor unit. Due to the torque-fixed coupling of the motor rim 4 to the compressor rim 12 , this relative alignment of the cylinders 6, 14 to one another remains constant during the operation of the motor-compressor unit 1.
  • This embodiment makes it easier for the rotary compressor 3 and the rotary motor 2 to be fluidically connected to one another by means of turbo pipes 23 .
  • This embodiment is based on the idea of using the rotary compressor 3 as a kind of turbocharger for the rotary engine 2 .
  • the rotary compressor 3 has a gas outlet opening 24 on each of its cylinders 14 or on their outer ends facing away from the compressor axis 13 .
  • This gas outlet opening 24 serves to discharge gas compressed by means of the rotary compressor 3 from the associated compression chamber of the respective cylinder 14 .
  • the gas compressed in this way can now be routed directly to the corresponding gas inlet opening 25 of the associated cylinder 6 of the rotary engine 2 by means of the respectively associated turbo pipe 23 .
  • the turbo tubes 23 are each formed by a straight piece of tube, with the gas flowing through a turbo tube 23 not being deflected. Viewed over their axial length, the turbo tubes 23 have a variable cross section.
  • an atomized or gaseous fuel can be fed into a respective turbo pipe 23 , so that the filling of the combustion chamber 26 of the associated cylinder 6 of the rotary engine 2 takes place with the aid of the gas flow of the gas compressed by means of the rotary compressor 3 .
  • the rotary motor 2 and the rotary compressor 3 are arranged axially offset along the transmission axis 9 .
  • the rotary motor 2 and the rotary compressor 3 are connected to one another by means of a transmission device 10 .
  • the connection between the rotary motor 2 and the rotary compressor 3 takes place in a torque-transmitting manner, so that the rotation of the rotary motor 2 is transmitted directly to the rotary compressor 3 .
  • the transmission device 10 has several struts that run parallel to the transmission axis 9 and create a fixed connection between the rotary motor 2 and the rotary compressor 3 .
  • the transmission device 10 is in particular based on figure 3 good to see.
  • the rotary motor 2 is started and thereby set in motion.
  • This movement of the rotary motor 2 includes a rotation of the motor rim 4 about the motor axis 5.
  • the circular movement of the motor rim 4 about the motor axis 5 is in figure 1 recognizable by means of the circular path 39 drawn there in dashed lines.
  • the motor pistons 7 Due to the eccentricity 41 between the motor axis 5 and the piston axis 11 , the motor pistons 7 also rotate.
  • the stroke movement of the motor pistons 7 forces the rotation of the motor rim 4, so to speak, since the motor pistons 7 can only avoid the axial force acting on them by rotating about the piston axis 11 and "drag along" the motor rim 4 .
  • the engine pistons 7 in their respective cylinders 6 continuously perform stroke movements.
  • the engine pistons 7 move on an in figure 1 Circular path 40 shown, the center of which is arranged at a distance from the center of the circular path 39 about the eccentricity 41 .
  • the movement of the engine rim 4 is initiated by the combustion of a fuel in the combustion chamber 26 of the cylinder 6 .
  • the motor axis 5 and the piston axis 11 remain stationary during operation of the rotary motor 2 , ie they do not move.
  • the result of this is that the connecting rod disk 34 to which the individual connecting rods 8 and the master connecting rod 32 are connected rotates equally about the piston axis 11 .
  • the master connecting rod 32 is attached to a center point of the connecting rod disk 34 , the connection between the master connecting rod 32 and the connecting rod disk 34 being designed in a torque-transmitting manner.
  • the remaining connecting rods 8 are each connected to the connecting rod disk 34 in an articulated manner.
  • the remaining connecting rod 8 in the static sense than Running pendulum rods, since they are connected both by means of the piston joints 30 to the engine piston 7 and to the connecting rod 34 in an articulated manner.
  • the rotary compressor 3 also has corresponding connecting rods 8, 32 , which guide the compressor ring 12 as the compressor ring rotates Cause compressor piston 15 within the cylinder 14 of the rotary compressor 3 .
  • the rotary compressor 3 also has a connecting rod disk 34 which is arranged eccentrically and which is offset by an eccentricity 41 in relation to a compressor axis 13 of the rotary compressor 3 .
  • the rotary motor 2 and the rotary compressor 3 are arranged along a common transmission axis 9 ; that is to say that the motor axis 5 and the compressor axis 13, around which the motor ring 4 and the compressor ring 12 revolve, coincide. It is particularly advantageous for this construction to arrange the rotary motor 2 and the rotary compressor 3 on a common support shaft. Since both the rotary engine 2 and the rotary compressor 3 are, in a manner of speaking, a kinematic inverted version of a typical piston engine, this carrier shaft can also be regarded as a stationary crankshaft 18 . This crankshaft 18 is particularly good figure 4 .
  • crankshaft 18 is stationary during operation of the motor-compressor unit 1 .
  • both the shaft as such and its bends, which are formed here in the form of pins 33 are stationary when the motor/compressor unit 1 is in operation.
  • the connecting rod disks 34 of the rotary motor 2 and the rotary compressor 3 described above are arranged on these pins 33 and rotate around them.
  • the central axes of the pins 33 coincide with the piston axes 11, 17 of the rotary motor 2 and the rotary compressor 3 , respectively.
  • a representation of Crankshaft 18, which includes the connecting rod disks 34 of the rotary engine 2 and the rotary compressor 3 is figure 5 removable.
  • crankshaft 18 is not used to transmit torque between the rotary engine 2 and the rotary compressor 3.
  • the transmission device 10 which has already been described above, is exclusively responsible for this.
  • the offsets of the crankshaft 18, that is to say the pins 33, are arranged offset relative to the transmission axis 9 , as viewed.
  • the pins 33 of the crankshaft 18 are arranged directly opposite each other relative to the transmission axis 9 , so that when a respective engine piston 7 is in its upper reversal position, the compressor piston 15 corresponding to this engine piston 7 is exactly in its lower reversal position. It goes without saying that, conversely, when a motor piston 7 is in its lower reversal position, the associated compressor piston 15 is in its upper reversal position.
  • This arrangement of the engine pistons 7 and the compressor pistons 15 relative to one another offers the advantage that the rotary compressor 3 can be used as a turbocharger for the rotary engine 2 .
  • This is based on the following consideration: when a motor piston 7 is in its lower reversing position, the motor piston 7 releases the gas inlet opening 25 of the cylinder 6 in the associated cylinder 6 .
  • the compressor piston 15 of the associated cylinder 14 of the rotary compressor 3 is in its upper reversing position, in which the gas in the compression chamber is compressed to the maximum.
  • the rotary motor 2 has an elevation 21 on an inner lateral surface 19 of its motor housing, which elevation extends radially to the motor axis 5.
  • This elevation 21 is designed in such a way that a radially measured distance between the motor axis 5 and a high point of the elevation 21 is less than a radially measured distance between the motor axis 5 and the inner lateral surface 19 of the motor housing outside of the elevation 21.
  • the elevation 21 extends over a partial angular range 20 of a complete revolution, ie 360°, of the motor housing.
  • the elevation 21 is designed to be continuous, so that there is no jump in cross section between the inner lateral surface 19 and the elevation 21 .
  • the elevation 21 is also asymmetrical, with a measured radial height of the elevation 21 continuously increasing to a certain extent from zero to a high point of the elevation 21 and then decreasing back to zero in the same way. In other words, the elevation 21 has a "run-in area".
  • the design of the elevation 21 follows the basic idea that a valve device 27 mounted circumferentially in the motor housing is forced to be guided radially inwards by engaging with the elevation 21 , i.e. in the direction of the motor axis 5. This guidance of a valve device takes place solely on the basis of being guided past the same along the elevation 21. Thus, there is a purely mechanical control of the valve device.
  • a corresponding roller 29 which is part of a valve device 27 , is mounted in this guide groove 35 .
  • this valve device 27 also includes a pin-like shaft and a valve disk 28. The latter is used directly to seal an associated cylinder 6 of the rotary engine 2.
  • valve devices 27 are in particular made of figure 1 removed, where they are shown there in engagement with the associated motor rim 4 .
  • the representations according to figures 6 and 7 only show the motor-compressor housing 22 together with the valve device in 27, without showing the rotary motor 2 and the rotary compressor 3 .
  • valve device in 27 In the course of the rotation of the rotary motor 2 , the valve device in 27 is guided with its roller 29 along the guide groove 35 , sweeping over the elevation 21 once with each revolution. As a result, the valve disk 28 of a valve device 27 is lifted once during one revolution of the rotary engine 2 from its associated sealing seat on the associated cylinder 6 and consequently the combustion chamber 26 is fluidically connected to an environment of the cylinder 6 . This makes it possible to conduct gases from the combustion chamber 26 out of the cylinder 6 .
  • an exhaust pipe 31 is advantageously arranged at an upper valve opening of each cylinder 6 of the motor rim 4 , through which the exhaust gases can then escape in a guided manner.
  • a closure of the valve that is to say a pressing of the valve disk 28 onto its associated sealing seat, takes place automatically after the elevation 21 has been passed, solely as a result of the prevailing centrifugal forces.
  • a mechanical feedback for example by means of a spring element, is not necessary.
  • the valve device in 27 is held in the guide groove 35 by the effect of centrifugal force with its roller 29 and is only forced radially inward in the direction of the motor axis 5 when the elevation 21 is passed. resulting in the opening mechanism described.
  • the rotary compressor 3 is also equipped with a corresponding elevation 21, guide groove 35 and associated valve device in 27 . Due to the staggered arrangement of the piston axes 7, 11 of the rotary motor 2 and the rotary compressor 3 , the elevations 21 in the motor/compressor housing 22 are arranged in an equally staggered manner corresponding to the angular offset of the piston axes 7, 11 . In this example, the projections 21 are opposite to each other in the motor-compressor housing 22 when viewed relative to the transmission axis 9 .
  • the control of the valve device in 27 of the rotary compressor 3 enables the gas compressed in the respective compression chamber to be released and thus allows it to flow out of the gas outlet opening 24 into the turbo pipe 23.
  • the motor/compressor housing 22 has appropriately positioned openings 36 according to FIG figure 7 are distributed over the circumference of the motor-compressor housing 22 .
  • the crankshaft 18 of the motor-compressor unit 1 is fixed by means of a positive-locking element 37 in opposite end walls of the motor-compressor housing 22 and is mounted in a torsion-proof manner. The form fit causes the crankshaft 18 actually is fixed together with the motor-compressor housing 22 and does not rotate about the transmission axis 9 .
  • the rotary compressor 3 is used exclusively for charging the rotary motor 2 . It goes without saying that the rotary compressor 3 is not necessary for operation of the rotary motor 2 , but is very advantageous.
  • the axial arrangement of rotary machines along a common axis offers the significant advantage that it is easily conceivable to combine further rotary machines with the motor-compressor unit 1 shown here or, for example, with an isolated rotary motor 2 . It is thus conceivable, for example, to transmit torque from the motor-compressor unit 1 shown to a further rotary compressor by means of gear wheels, so that this further rotary compressor can be operated in a manner analogous to the rotary compressor 3 described.
  • a further rotary compressor acts as a compressor in an otherwise conventional compression refrigeration machine, that is to say, in other words, the motor-compressor unit 1 can be used as a drive element for an air conditioning system.
  • a torque-locking engagement of the respective rotary motor or of a plurality of rotary motors coupled to one another and with the associated rotary compressor can be selectively activated and deactivated. This can be done, for example, by means of a clutch, so that it is up to the user of the respective motor-compressor unit to activate or deactivate one or more rotary compressors as desired. It is also conceivable to provide several rotary motors, with one or more further rotary motors being "switched on" in addition to a first rotary motor merely as a function of a required power.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Claims (9)

  1. Ensemble moteur-compresseur (1), comprenant
    - au moins un moteur rotatif (2), ainsi
    - qu'au moins un compresseur rotatif (3), destiné à comprimer au moins un fluide gazeux,
    le moteur rotatif (2) comprenant
    - un carter de moteur, pourvu d'au moins une couronne (4) de moteur, logée de manière rotative dans le carter de moteur, qui est logée en rotation autour d'un axe (5) de moteur du carter de moteur,
    - au moins un cylindre (6), qui est placé dans la couronne (4) de moteur, dans le cylindre (6) étant placé un piston (7) de moteur, qui délimite, conjointement avec une paroi du cylindre (6) une chambre de combustion (26) du cylindre (6), le piston (7) de moteur étant guidé en mobilité linéaire dans le cylindre (6) au moyen d'une bielle (8), ainsi
    - qu'au moins un axe (11) de piston, autour duquel l'au moins un piston (7) de moteur est rotatif, de sorte que le piston (7) de moteur se déplace sur une trajectoire circulaire (40) pendant un fonctionnement du moteur rotatif (2),
    l'axe (11) de piston étant orienté à la parallèle de l'axe (5) de moteur et étant placé en étant écarté de l'axe (5) de moteur, de sorte qu'au cours d'une rotation de la couronne (4) de moteur autour de l'axe (5) de moteur, l'au moins un piston (7) de moteur effectue à l'intérieur du cylindre (6) un déplacement ascendant et descendant cyclique, le compresseur rotatif (3) comprenant
    - un carter de compresseur, pourvu d'au moins une couronne (12) de compresseur, logée de manière rotative dans le carter de compresseur, qui est logée en rotation autour d'un axe (13) de compresseur du carter de compresseur,
    - au moins un cylindre (14), qui est placé dans la couronne (12) de compresseur, dans le cylindre (14) étant placé un piston (15) de compresseur, qui délimite, conjointement avec une paroi du cylindre (6) une chambre de compression du cylindre (14), le piston (15) de compresseur étant guidé en mobilité linéaire dans le cylindre (14) au moyen d'une bielle (16), ainsi
    - qu'au moins un axe (17) de piston, autour duquel l'au moins un piston (15) de compresseur est rotatif, de sorte que le piston (15) de compresseur se déplace sur une trajectoire circulaire (40) pendant un fonctionnement du compresseur rotatif (3),
    l'axe (17) de piston étant orienté à la parallèle de l'axe (13) de compresseur et étant placé en étant écarté de l'axe (13) de compresseur, de sorte qu'au cours d'une rotation de la couronne (12) de compresseur autour de l'axe (13) de compresseur, l'au moins un piston (15) de compresseur effectue à l'intérieur du cylindre (14) un déplacement ascendant et descendant cyclique,
    le moteur rotatif (2) et le compresseur rotatif (3) étant susceptibles d'être accouplés l'un à l'autre, de manière à transmettre le couple au moyen d'un système de transmission (10),
    caractérisé en ce que
    le carter de moteur et le carter de compresseur comportent chacun sur leurs surfaces d'enveloppe (19) intérieures une élévation (21) s'étendant en direction radiale vers l'intérieur sur une plage angulaire partielle (20), l'au moins un cylindre (6) du moteur rotatif (2) et l'au moins un cylindre (14) du compresseur rotatif (3) comportant chacun au moins un système de soupapes (27) au moyen duquel, pendant le fonctionnement de l'ensemble moteur-compresseur (1), des fluides peuvent être évacués hors de la chambre de combustion (26) du moteur rotatif (2) ou du gaz comprimé peut être évacué hors de la chambre de compression du compresseur rotatif (3), et le système de soupape (27) s'engageant sur au moins une plage angulaire partielle (20) d'un tour complet du cylindre (6) au-delà de l'axe (5) de moteur dans le carter de moteur, au moyen de l'engagement, au moins un élément de soupape du système de soupape (27) pouvant être forcé hors de son siège d'étanchéité, de sorte qu'une liaison fluidique entre la chambre de combustion (26) du cylindre (6) et un environnement soit susceptible d'être libérée, ou soit libérée et au moins un tuyau turbo (23), au moyen duquel une liaison fluidique est susceptible d'être établie ou est établie entre un orifice (24) de sortie de gaz du compresseur rotatif (3) et un orifice (25) d'entrée de gaz du moteur rotatif (2), de sorte qu'au moins une partie du gaz comprimé au moyen du compresseur rotatif (3) soit susceptible d'être alimentée au moyen du tuyau turbo (23) vers une chambre de combustion (26) de l'au moins un cylindre (6) du moteur rotatif (2).
  2. Ensemble moteur-compresseur (1) selon la revendication 1, caractérisé en ce qu'un axe (9) de transmission du système de transmission (10), autour duquel le système de transmission (10) tourne pendant un fonctionnement de l'ensemble moteur-compresseur (1) coïncide avec l'axe (5) de moteur et l'axe (13) de compresseur.
  3. Ensemble moteur-compresseur (1) selon la revendication 1 ou 2, caractérisé en ce que le moteur rotatif (2) et/ou le compresseur rotatif (3) sont logés au moyen d'un vilebrequin (18) stationnaire, un axe du vilebrequin (18) et l'axe (11, 17) de piston du moteur rotatif (2) ou du compresseur rotatif (3) étant placés à la parallèle l'un de l'autre et en étant écartés l'un de l'autre.
  4. Ensemble moteur-compresseur (1) selon la revendication 3, caractérisé en ce que le moteur rotatif (2) et le compresseur rotatif (3) sont logés avec un décalage axial le long d'un vilebrequin (18) stationnaire commun, de préférence les axes (11, 17) de piston du moteur rotatif (2) et du compresseur rotatif (3) étant placés à la parallèle l'un de l'autre et en étant écartés l'une de l'autre sur le vilebrequin (18), de manière préférentielle par ailleurs, considérés dans un plan perpendiculaire à l'axe de vilebrequin et par rapport à l'axe de vilebrequin du vilebrequin (18), les axes (11, 17) de piston étant opposés.
  5. Ensemble moteur-compresseur (1) selon l'une quelconque des revendications 1 à 4, caractérisé en ce que, considérées par rapport à l'axe (5) de moteur ou à l'axe (13) de compresseur, l'élévation (21) du carter de moteur et l'élévation (21) du carter de compresseur sont placées en étant décalées l'une par rapport à l'autre de la valeur d'un angle de décalage le long de la surface d'enveloppe (19) intérieure respective du carter respectif.
  6. Ensemble moteur-compresseur (1) selon l'une quelconque des revendications 1 à 5, caractérisé en ce que le moteur rotatif (2) et le compresseur rotatif (3) sont réunis dans un carter moteur-compresseur (22) commun.
  7. Ensemble moteur-compresseur (1) selon l'une quelconque des revendications 1 à 6, caractérisé par un ensemble générateur, destiné à transformer de l'énergie cinétique en énergie électrique ou inversement, l'ensemble générateur comprenant au moins un carter de générateur dans lequel un rotor est logé en rotation autour d'un arbre de générateur du carter de générateur, l'arbre de générateur étant susceptible d'être accouplé au moins temporairement de manière à transmettre la force avec le système de transmission (10) .
  8. Ensemble moteur-compresseur (1) selon l'une quelconque des revendications 1 à 7, caractérisé par une rainure de guidage (35), qui est placée en périphérie et de manière fermée sur soi sur la surface d'enveloppe (19) intérieure du carter de moteur et/ou du carter de compresseur et avec laquelle l'élévation (21) respectivement associée coopère.
  9. Ensemble moteur-compresseur (1) selon l'une quelconque des revendications 1 à 8, caractérisé en ce que le système de soupape (27) comporte un galet de roulement (29) ou un chariot de guidage, au moyen duquel le système de soupape (27) coopère avec la rainure de guidage (35).
EP17158650.6A 2016-03-01 2017-03-01 Unité moteur-compresseur Active EP3214262B1 (fr)

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US20170254320A1 (en) 2017-09-07
EP3214262A3 (fr) 2017-11-22
EP3214262A2 (fr) 2017-09-06
US10598168B2 (en) 2020-03-24
DE102016103615B3 (de) 2017-08-24

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