EP0240467B1 - Machine alternative à pistons rotatifs - Google Patents

Machine alternative à pistons rotatifs Download PDF

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Publication number
EP0240467B1
EP0240467B1 EP87810206A EP87810206A EP0240467B1 EP 0240467 B1 EP0240467 B1 EP 0240467B1 EP 87810206 A EP87810206 A EP 87810206A EP 87810206 A EP87810206 A EP 87810206A EP 0240467 B1 EP0240467 B1 EP 0240467B1
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EP
European Patent Office
Prior art keywords
piston
cylinder
working
engine
pistons
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EP87810206A
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German (de)
English (en)
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EP0240467A1 (fr
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Iso Wyrsch
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Individual
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Individual
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Priority to AT87810206T priority Critical patent/ATE68556T1/de
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    • 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
    • F01B3/00—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F01B3/0079—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis having pistons with rotary and reciprocating motion, i.e. spinning pistons
    • 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
    • F01B3/00—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F01B3/04—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis the piston motion being transmitted by curved surfaces
    • F01B3/06—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis the piston motion being transmitted by curved surfaces by multi-turn helical surfaces and automatic reversal
    • F01B3/08—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis the piston motion being transmitted by curved surfaces by multi-turn helical surfaces and automatic reversal the helices being arranged on the pistons
    • 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
    • F02B75/00—Other engines
    • F02B75/26—Engines with cylinder axes coaxial with, or parallel or inclined to, main-shaft axis; Engines with cylinder axes arranged substantially tangentially to a circle centred on main-shaft axis
    • 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
    • F02B75/00—Other engines
    • F02B75/02—Engines characterised by their cycles, e.g. six-stroke
    • F02B2075/022—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle
    • F02B2075/025—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle two
    • 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
    • F02B75/00—Other engines
    • F02B75/02—Engines characterised by their cycles, e.g. six-stroke
    • F02B2075/022—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle
    • F02B2075/027—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle four
    • 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
    • F02B3/00—Engines characterised by air compression and subsequent fuel addition
    • F02B3/06—Engines characterised by air compression and subsequent fuel addition with compression ignition

Definitions

  • the "classic”, well-known reciprocating piston machine has pistons that only make a reciprocating movement.
  • the piston movement is usually generated by the crankshaft and connecting rod.
  • the disadvantages of the classic reciprocating piston machine include the friction of the reciprocating piston on the cylinder, the space required for the crank mechanism and the need for separate organs to control the inlets and outlets.
  • Rotary reciprocating piston machine here means a work machine or an engine.
  • the rotary reciprocating piston machine from Wilfried Schwant also controls the slots by the rotary and reciprocating motion of the piston, but in a different way:
  • the piston has a channel that leads inside the piston from the piston face to the side surface of the piston .
  • the channel connects the working area with the cylinder wall and, depending on the piston position, with the slots in the cylinder wall.
  • the rotary reciprocating piston machine from Joe Burrough (US 2,473,936) also has pistons which perform a rotary reciprocating movement, but the control of the slots is not influenced by the rotary movement of the piston.
  • a cam track rotates relative to guide elements and thereby makes a rotary stroke movement relative to the guide elements.
  • Either this cam track is on the piston and the guide elements in the form of rollers etc. are attached to the cylinder (Maltby, Burrough, Schwandt), or vice versa.
  • a problem with the previous rotary reciprocating machines with control of the inlet and outlet openings by the piston is the large dead space at the top dead center.
  • a high compression ratio is therefore not possible.
  • the reason for the large dead space lies in the design principle: In order to realize a small dead space in the top dead center, the shape of the cylinder head would have to correspond approximately to the negative shape of the piston surface. However, this is only possible approximately because otherwise the non-rotating cylinder head hinders the non-rotationally symmetrical piston in its top dead center during its rotational movement.
  • a second problem is that the changing pressure of the working medium causes an alternating force in the radial direction on the asymmetrical piston. If the piston is pressed against the cylinder wall, this increases the friction.
  • some of the advantages offered by the rotary stroke movement of the piston have not been consistently exploited. It is therefore the object of the present invention to provide a rotary reciprocating piston machine which, with its various designs, eliminates the problems mentioned.
  • the end face of the pistons facing the working space is additionally shaped in such a way that the radial force components on the piston end face resulting from the pressure of the working medium compensate each other, so that only one axial force is applied the piston results (see claim 2).
  • Figures 1a and 1b is a longitudinal section of a machine along the axis of a cylinder with the cylinder parts 1a, 1b, 1c. The machine is shown in two different positions by half a shaft revolution (Fig. 1a and 1b).
  • the cylinder has openings (slots) in its wall, which are provided for the inlet (8, 10) and for the Outlet (9, 11) of the working medium.
  • the slots are opened and closed by the pistons (2) and by the piston-like members (5).
  • the rotary piston machine of Figure 1 is shown as a 2-stroke internal combustion engine. If the arrangement of the slots were changed, however, this rotary piston machine could function differently, for example as a compressor.
  • the piston (2) makes an oscillating stroke movement and at the same time a rotary movement around the cylinder axis.
  • the piston-like member (5) only rotates around the cylinder axis.
  • the variant shown has 4 work rooms (7a and 7b).
  • the position shown shows two working spaces (7a) at maximum volume, corresponding to the bottom dead center.
  • the other two work spaces (7b) have at the moment called the minimum volume, dead space or compression space, corresponding to the top dead center. Because the end faces simultaneously rotate and fit together according to the invention, the dead space is very small.
  • Figure 1b shows the pistons in other positions after half a revolution.
  • the movement of the rotary piston (2) is generated in a known manner by a cam track (3), which is supported on the guides (4).
  • the pistons (2) make one stroke cycle, i.e. a reciprocating movement, per revolution.
  • the power is transferred from the piston to the outside by means of a central shaft (14).
  • the pistons (2) are connected to the central shaft (14) so that they are longitudinally displaceable along the central shaft, but that they transmit the torque to the central shaft (14).
  • Figure 2 shows schematically a section through the cylinder axis of a rotary reciprocating machine, in which the lifting movement of the piston (2) is generated in a known, conventional manner by means of a crankshaft (28), connecting rod (27) and crosshead (25).
  • the rotation of the piston (2) is generated in a separate manner.
  • the rotary motion through a gear (22) and a central shaft (14) on the piston (2) and the piston-like member (5) transferred.
  • the arrangement and the shape of the piston and the piston-like member and the manner in which the openings in the cylinder wall are controlled are designed according to the invention and are analogous to FIG. 1.
  • Figure 3 illustrates the charge change in a rotary reciprocating machine which works as a pump.
  • a cross section through the working space (7) in the cylinder (1) with a view of the piston face is shown schematically.
  • Fig. 3a The piston is at top dead center, the inlet slot (8) and the outlet slot (9) are closed by the piston.
  • Fig. 3b The inlet slot is opened by the piston, the piston goes down, the working medium flows in (10).
  • Fig. 3c The piston is approximately at bottom dead center.
  • the inlet slot is just closed, the outlet slot is not yet open.
  • Fig. 3d The piston comes up, the outlet (9) is open, the working medium flows out (11).
  • FIG. 4 shows, analogously to FIG. 3, the charge exchange in the case of a 4-stroke engine.
  • 4a top dead center
  • 4b suction
  • 4c bottom dead center
  • 4d compacting
  • 4e start of combustion and top dead center
  • 4f work cycle
  • 4g bottom dead center
  • 4h exhaust.
  • FIG. 5 shows schematic examples of shapes of pistons (2) or piston-like members (5):
  • FIGS. 5a and 5b show asymmetrical shapes; 5c and d, 5e and 5f show point-symmetrical shapes, in which the pressure in the working space does not result in a resulting transverse force.
  • Figures 6 to 9 show variants of the mechanism which leads the piston (2) to the rotary-stroke movement.
  • the spatial cam track (3) is fixed to the piston (2) as a disk-like cam track.
  • the guides here consist of rollers (4).
  • the piston (2) makes one stroke cycle per revolution. This version corresponds to the current state of the art.
  • the spatial cam track (3) is shaped as a circumferential groove in which the guide (4) engages. This version also corresponds to the prior art.
  • FIGS. 9a-9c show details of an improved embodiment from three viewing directions.
  • the guides (4) are connected to one another by rockers (16), the rockers are connected to the cylinder (see FIG. 7).
  • FIGS. 10a-c show an example of the shape of the end faces of pistons (2) or of piston-like members (5) which can be used for the machine according to the invention.
  • Figure 10c shows a view from the working area on the piston end.
  • Figure 10a and 10b show a detail from a section along the cylinder axis in the direction of AA and BB.
  • the piston (2) moves to the top dead center.
  • the working medium pressed out of the narrow squeezing surfaces is introduced tangentially into the toroidal swirl space (43). Such a swirling of the working medium is desirable for diesel engines, for example.
  • FIGS. 11 and 12 schematically show the torque transmission between the central shaft (14) and the rotary reciprocating piston (2) by means of a membrane (18) or by means of a bellows (19).
  • FIG. 13 schematically shows an example of an embodiment of additional inner working spaces (47) according to the invention in the piston (2).
  • the inner piston (31) is fixed on the central shaft (14) and makes a rotational movement.
  • the piston (2) serves the inner piston (31) as a cylinder and increases and decreases by its rotary-stroke movement the inner working spaces (47) on both sides of the inner piston (31).
  • an inlet duct (30) in the central shaft (14) leads via non-return valves (32) into the inner working spaces (47).
  • the outlet takes place through slots (33) in the piston (2) and in the cylinder (1), which are opened and closed by the movement of the piston (2).
  • the inner work spaces can e.g. can be used as a pump or compressor, or, for example, to pre-compress the working medium and to guide it from the inner working spaces (47) through a special channel (34) into the working spaces (7).
  • the end faces of the inner piston (31) and the inner shape of the piston (2) are advantageously matched to one another in such a way that the dead space is small.
  • the working space is delimited by the cylinder (1; 1a, 1b, 1c) and either by two pistons (2) or by a piston (2) and a piston-like member (5).
  • the pistons (2) rotate around the cylinder axis and additionally make an oscillating stroke movement along the cylinder axis.
  • the piston-like member (5) only rotates around the cylinder axis.
  • At least one piston (2) or a piston-like member (5) controls one or more slots in the cylinder wall by covering or uncovering these slots with its outer surface. The frontal boundary of this lateral surface is not rotationally symmetrical. Therefore, the rotary movement has an effect on the opening and closing of the slots.
  • the dead space in top dead center can be made as small as desired.
  • the dead space is almost zero:
  • the two pistons or the piston and the piston-like member fit exactly into one another with their end faces like a negative form and a positive form. Because both parts rotate in the cylinder, there is no impediment to the rotary movement.
  • this invention can be used for all known applications of piston machines.
  • 2-stroke, 4-stroke engines, pumps and compressors, etc. which are realized according to this principle, are therefore only different types of embodiment of the same idea according to the invention.
  • a version according to the invention avoids the second disadvantage of previous rotary reciprocating piston machines with control of the slots by the piston: it avoids the resulting radial force component which the pressure of the working medium exerts on the non-rotationally symmetrical piston end face.
  • the piston is additionally shaped such that the radial transverse force components cancel each other out.
  • the piston (2) of another version also makes a rotary-stroke movement and serves with its inner surface as a cylinder for an additional inner piston (31) enclosed therein.
  • This inner piston is attached to a shaft or axis which extends into the piston (2) or passes through the piston (2).
  • This inner piston (31) therefore executes a lifting movement relative to the piston (2) surrounding it, as a result of which this inner system also functions as a power or working machine and is used, for example, to pre-compress the working medium.
  • Figure 13 schematically shows an embodiment thereof).
  • Another version is characterized in that a plurality of inlet slots or a plurality of outlet slots or a plurality of inlet slots and a plurality of outlet slots per working space exist in the cylinder wall, and in that these inlet slots and / or these outlet slots are not opened and closed together at the same time.
  • This is achieved by arranging the slots in the cylinder wall in such a way that the piston or the piston-like member opens or closes them one after the other, or by valves or valve-like devices which additionally open or close at least one of these slots. Examples of this will be mentioned below in connection with "Examples for carrying out the invention”.
  • Another version is characterized in that the working medium is set in rotation or swirled in the working space: This movement of the working medium is caused by the rotational movement of the end faces of the piston (2) or the piston-like member (5) and by the direction of the inlet channel or of the inlet channels (8) which have a tangential component relative to the cylinder axis.
  • Additional rotation or swirling of the working medium can be caused near the top dead center by the shape of the two end faces.
  • the working medium is introduced into a swirl space between these two end faces. (See Figure 10a-c).
  • the synchronization between the rotary movement and the stroke movement of the piston is variable.
  • the control times of the slot control are changed, for example.
  • This adjustable synchronization is done in the following way: That part of the device to generate the rotary stroke movement of the piston, which is directly or indirectly attached to the cylinder (1), is rotatable relative to the cylinder about the cylinder axis, or that part of the device which is attached to the piston (2) is rotatable about the axis of rotation of the piston and therefore also relative to the end face of the piston.
  • a central shaft (14) transmits the rotary movement of the piston (2) to one or two outer end faces of the machine. It is made in such a way that a torque is transmitted between the piston (2) and the central shaft (14) and that the oscillating stroke movement is nevertheless ensured by an axial displacement.
  • This is achieved according to the invention by means of rolling elements which transmit tangential forces and move in a rolling manner during the axial displacement. Constructions of such elements are known as longitudinally displaceable homokinetic joints which are used for the front wheel drive of cars.
  • the torque transmission from the piston (2) to the central shaft (14) or the torque transmission between two adjacent pistons (2) takes place by means of one or more diaphragms or bellows or other spring-like elements which allow the axial longitudinal displacement by elastic deformation.
  • the piston-like member (5) also forms a component, e.g. the anchor, an electric motor or an electric generator.
  • the other component e.g. the stator, the electric motor or generator is attached directly or indirectly to the cylinder. In this way, electromagnetic forces act in a tangential direction on this rotating member.
  • the torque transmission between the piston (2), or between the piston (2) and the piston-like member (5) takes place by means of a positive fit, in that the adjacent end faces of these parts (2 or 5) as Interlocking claws.
  • the shape of these end faces is matched to the stroke length in such a way that they remain in engagement with one another and in this way transmit tangential forces by means of sliding surfaces.
  • Another version is characterized in that the pistons (2) and, if present, the piston-like member (5) rest on a lubricating film which is located in that region of the cylinder wall where there are no slots (8/9) to be controlled.
  • the rotational movement of these parts (2 and 5) creates a hydrodynamic lubrication state.
  • a sealing element e.g. a scraper ring mounted in the cylinder so that the lubricant can get into the work area or into the slots.
  • the choice of the embodiment of the invention depends on the size, the use, the working method of the machine and so on.
  • embodiments of the rotary reciprocating piston machine according to the invention in use as an internal combustion engine are described because the use and function of piston engines as an internal combustion engine are best known:
  • the working space (7) is delimited by two pistons (2), both of which perform a rotary stroke movement. This has the advantage that the relative surface of the work area is small.
  • the two pistons control the inlet and outlet slots in the cylinder walls.
  • the pistons are shaped such that the compression ratio is as high as is desired for the application (for example gasoline engine) and that the pressure of the working medium does not exert any radial force on the pistons.
  • the first example relates to the exhaust process in an internal combustion engine which is charged by the exhaust gas energy, for example by means of a turbocharger.
  • the exhaust process looks as follows: When the exhaust opens, the pressure in the cylinder is many times higher than in the exhaust manifold in front of the turbocharger. The exhaust gas flows out at the speed of sound and is expanded to the pressure level of the exhaust manifold. As a result, a lot of useful energy is lost in this first phase of the exhaust. Later the pressure in the cylinder drops to the level of the exhaust manifold.
  • the rotary piston machine according to the invention works as follows: When the first outlet opens, the exhaust gas flows into an exhaust manifold, in which the pressure is relatively high. If the pressure in the exhaust manifold does not exceed approximately half the cylinder pressure, the speed of sound is still achieved.
  • the piston opens a second outlet channel, which leads the exhaust gases into another exhaust manifold, in which the pressure is lower.
  • the first exhaust port is closed.
  • the second outlet duct leads directly to the outside via a silencer. Or the exhaust gases are first led through additional outlet slots into additional different exhaust manifolds with different pressure levels to turbochargers. Because of the higher exploitation of the exhaust gas energy in the In the first phase, the turbo receives enough energy and therefore does not require the entire amount of exhaust gas.
  • the cylinder internal pressure is now significantly lower than the compressed intake gas in the late phase of the exhaust. With a four-stroke engine, this results in a noticeable additional performance and an improvement in efficiency even during the gas change. With the two-stroke engine you can achieve an extremely fast and effective gas change.
  • the exhaust system mentioned in the example above also provides a clear advantage for the "cooperation" between engine and turbo and for the characteristics of the engine's power output:
  • the first exhaust is designed, for example, so that the exhaust gas during full load and rather low speed during the opening time of the first outlet, flows out at the speed of sound.
  • the absolute duration of the opening time of the first outlet is reduced linearly with the speed. For this, the number of openings per unit of time increases linearly.
  • the boost pressure drops. The engine torque therefore increases with decreasing speed.
  • additional slots During compression, pre-compressed additional air or a fuel-air mixture is blown into the work area through a special inlet slot.
  • the fuel or a fuel-air mixture is only added to the intake air when the outlet is closed. This prevents unburned fuel from being emitted.
  • the ability of the piston to cover openings or areas in the cylinder wall can also be used to protect valves, nozzles, igniters, sensors, etc. from the high combustion temperature or pressure.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Combustion & Propulsion (AREA)
  • Chemical & Material Sciences (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Hydraulic Motors (AREA)
  • Reciprocating Pumps (AREA)
  • Reciprocating, Oscillating Or Vibrating Motors (AREA)
  • Compressor (AREA)
  • Connection Of Motors, Electrical Generators, Mechanical Devices, And The Like (AREA)
  • Lubrication Of Internal Combustion Engines (AREA)
  • Pistons, Piston Rings, And Cylinders (AREA)
  • Transmission Devices (AREA)
  • Forklifts And Lifting Vehicles (AREA)
  • Massaging Devices (AREA)

Claims (12)

  1. Machine à pistons, utilisable comme moteur ou comme machine, composée d'un cylindre (1), d'un premier piston (2), qui est guidé dans le cylindre (1) de sorte qu'il effectue un mouvement rotatif autour de l'axe du cylindre et en même temps un mouvement alternatif oscillant parallèle à l'axe du cylindre, d'un second piston (2) ou une pièce similaire (5) au piston, qui est guidé(e) dans le cylindre (1) de sorte qu'il (ou elle) effectue au moins un mouvement rotatif autour de l'axe du cylindre, l'arrangement étant de sorte que le cylindre (1), le premier piston (2), et le second piston (2) ou la pièce similaire (5) au piston limitent une chambre de travail (7) et qu'au moins l'arête de la face du premier piston (2) ou du second piston (2) ou de la pièce similaire (5) au piston, tournée vers la chambre de travail (7), commande un ou plusieurs orifices d'admission ou d'échappement (8, 9) de la chambre de travail (7), placés à la paroi du cylindre,
    caractérisée en ce que les faces du premier et du second piston (2) ou du premier piston (2) et de la pièce similaire (5) au piston, qui sont tournées vers la chambre de travail, sont formées de manière à ce que les lignes d'arêtes, qui limitent les faces vers la surface latérale des pistons (2) ou de la pièce similaire au piston (5) ne sont pas à symétrie de révolution par rapport à l'axe du cylindre, et que les deux faces des pistons (2) ou de la pièce similaire au piston (5), qui sont tournées vers la chambre de travail et qui limitent cette chambre de travail en sens axial, s'adaptent par rapport à leur formes et à leur position de manière qu'au point mort supérieur de la machine à piston la chambre de travail (7) peut être réduite à volonté.
  2. Machine à pistons selon la revendication 1, caractérisée par la face des pistons (2) qui est formée de manière à ce que les composantes de force radiales, qui proviennent de la pression du fluide moteur, se neutralisent de manière que seul une force axiale résulte sur le piston.
  3. Machine à pistons selon la revendication 1 ou 2, caractérisée par un piston (2) au moins, qui est creux et qui sert de cylindre par sa paroi intérieure pour un piston intérieur (31) qui est enfermé et qui est fixé sur un arbre central (14) s'étendant dans le piston ou passant par le piston et qui exécute un mouvement alternatif oscillant relatif au piston (2) qui l'entoure, le système intérieur agissant par cet effet comme machine à pistons.
  4. Machine à pistons selon la revendication 1, 2, ou 3, caractérisée en ce que le mouvement des pistons (2) est produit au moyen d'au moins un chemin incurvé (3), qui s'appuye sur un ou plusieurs guidages, consistant d'organes de guidage comme par exemple des rouleaux ou des glissières et fait un mouvement rotatif et alternatif relatif à ces guidages, et que ces organes de guidage (4) sont liés les uns aux autres avec des bascules (16).
  5. Machine à piston selon la revendication 1, 2, 3 ou 4, caractérisée en ce qu'il y a plusieurs orifices d'admission ou plusieurs orifices d'échappement, ou plusieurs orifices d'admission et plusieurs orifices d'échappement à la paroi du cylindre par chambre de travail et que ces orifices d'admission ou que ces orifices d'échappement ne sont pas ouverts ou férmés ensemble en même temps.
  6. Machine à piston selon la revendication 1,2,3,4 ou 5, caractérisée en ce que le fluide moteur dans la chambre de travail est mis en rotation ou est tourbilloné par le mouvement rotatif des faces tournées vers la chambre de travail et par la direction de l'orifice ou des orifices d'admission (8) ayant une composante tangentielle relativement à l'axe du cylindre.
  7. Machine à pistons selon la revendication 1, 2, 3, 4, 5 ou 6, caractérisée par la synchronisation entre la rotation du piston et le mouvement alternatif du piston, qui est variable, puisque cette partie du mécanisme causant le mouvement alternatif rotatif du piston, qui est fixée directement ou indirectement au cylindre (1), est mobile par rapport au cylindre autour de l'axe du cylindre, ou l'autre partie de ce mécanisme, qui est fixée au piston (2), est mobile par rapport à la face du piston autour de l'axe de rotation du piston.
  8. Machine à pistons selon la revendications 1, 2, 3, 4, 5, 6 ou 7, caractérisée en ce que le mouvement rotatif est transmis d'un des pistons (2) sur un autre piston (2), sur une pièce similaire (5) au piston et/ou à l'extérieur de la machine au moyen d'un arbre central (14) allant le long de l'axe du cylindre, le couple étant transmis du piston (2) sur l'arbre central (14) au moyen de rouleaux, qui transmettent des forces tangentielles et se meuvent de manière rotative durant la translation axiale comme des joints homocinétiques déplaçables longitudinalement.
  9. Machine à pistons selon la revendication 1, 2, 3, 4, 5, 6 ou 7, caractérisée en ce que le couple est transmis du piston (2) sur l'arbre central (14) ou directement entre deux pistons voisins au moyen d'une ou plusieurs membranes ou soufflets ou autres organes similaires à des ressorts qui permettent le déplacement axial en longeur par une déformation élastique.
  10. Machine à pistons selon la revendication 1,2,3,4,5, 6,7,8 ou 9, caractérisée en ce que la pièce similaire (5) au piston est créé de manière qu'il fait partie d'un moteur électrique ou d'un générateur électrique.
  11. Machine à pistons selon la revendication 1,2,3,4,5, 6,7 ou 10, caractérisée en ce que le mouvement rotatif est transmis entre les pistons (2) ou entre un piston (2) et une pièce similaire (5) au piston à engagement positif par les deux faces voisines limitant la chambre de travail.
  12. Machine à pistons selon la revendication 1,2,3,4,5, 6,7,8,9,10 ou 11, caractérisée en ce que les pistons (2) sont couchés sur un film lubrifiant, qui se trouve dans cette zone de la paroi du cylindre, où il n'y a pas d'orifices à commander, et que le lubrifiant est tenu à l'écart de la chambre de travail par un segment racleur ou par des autres systèmes d'étanchéité, s'il ne doit pas parvenir dans la chambre de travail.
EP87810206A 1986-04-04 1987-04-03 Machine alternative à pistons rotatifs Expired - Lifetime EP0240467B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT87810206T ATE68556T1 (de) 1986-04-04 1987-04-03 Dreh-hubkolben-maschine.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH1316/86 1986-04-04
CH131686 1986-04-04

Related Child Applications (2)

Application Number Title Priority Date Filing Date
EP90100552.0 Division-Into 1987-04-03
EP90100553.8 Division-Into 1987-04-03

Publications (2)

Publication Number Publication Date
EP0240467A1 EP0240467A1 (fr) 1987-10-07
EP0240467B1 true EP0240467B1 (fr) 1991-10-16

Family

ID=4207589

Family Applications (3)

Application Number Title Priority Date Filing Date
EP90100552A Expired - Lifetime EP0369990B1 (fr) 1986-04-04 1987-04-03 Moteur alternatif à pistons tournant
EP87810206A Expired - Lifetime EP0240467B1 (fr) 1986-04-04 1987-04-03 Machine alternative à pistons rotatifs
EP90100553A Expired - Lifetime EP0369991B1 (fr) 1986-04-04 1987-04-03 Moteur alternatif à pistons tournant

Family Applications Before (1)

Application Number Title Priority Date Filing Date
EP90100552A Expired - Lifetime EP0369990B1 (fr) 1986-04-04 1987-04-03 Moteur alternatif à pistons tournant

Family Applications After (1)

Application Number Title Priority Date Filing Date
EP90100553A Expired - Lifetime EP0369991B1 (fr) 1986-04-04 1987-04-03 Moteur alternatif à pistons tournant

Country Status (10)

Country Link
EP (3) EP0369990B1 (fr)
JP (1) JPH0794801B2 (fr)
KR (2) KR960000436B1 (fr)
AT (3) ATE68556T1 (fr)
AU (1) AU7209387A (fr)
CA (1) CA1308155C (fr)
DE (3) DE3788357D1 (fr)
ES (3) ES2048328T3 (fr)
GB (3) GB2198788B (fr)
WO (1) WO1987005964A1 (fr)

Families Citing this family (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4926639A (en) * 1989-01-24 1990-05-22 Mitchell/Sterling Machines/Systems, Inc. Sibling cycle piston and valving method
GB8907984D0 (en) * 1989-04-10 1989-05-24 Szyler Jan Rotary engine
NL9000078A (nl) * 1990-01-11 1991-08-01 Philips Nv Motor-compressor eenheid.
ATE163211T1 (de) * 1991-10-15 1998-02-15 Mansour Almassi Brennkraftmaschine mit rotierendem kolben
GB9210139D0 (en) * 1992-05-12 1992-06-24 Fisher Hugh E Piston and cylinder devices
GB2280710A (en) * 1993-08-04 1995-02-08 Keith Andrew Maclaughan Rotating and reciprocating piston i.c. engine.
GB2287753B (en) * 1994-03-22 1997-12-10 Joanne Spinks Two stroke engine
DE4424319C1 (de) * 1994-07-09 1996-02-22 Harald Hofmann Heißgasmotor
CZ219997A3 (cs) * 1997-07-11 1999-01-13 Pavel Wenzel Motor s vnějším spalováním
EP0978932A1 (fr) * 1998-08-06 2000-02-09 S.C. NDR Management S.r.l. Appareil ayant un rotor et un stator
JP2010531943A (ja) * 2007-06-18 2010-09-30 コールド パワー システムズ インコーポレイテッド エネルギー伝達機およびエネルギー伝達方法
PL2449263T3 (pl) 2009-07-02 2013-09-30 Haas Mondomix B V Urządzenie i sposób pompowania płynnych mas
EP3185989B1 (fr) 2014-08-25 2021-08-11 Basf Se Élimination du sulfure d'hydrogène et du dioxyde de carbone d'un flux de fluide
AT526919B1 (de) 2023-03-01 2024-09-15 Friedl Rainhard Kolbenmaschine

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB282125A (en) * 1926-07-19 1927-12-19 Cecil Law Improvements in or relating to two-stroke cycle internal combustion engines
US2352396A (en) * 1942-02-20 1944-06-27 Kenneth R Maltby Internal-combustion engine
US2532106A (en) * 1946-12-06 1950-11-28 Korsgren Theodore Yngve Multiple opposed piston engine
US2473936A (en) * 1947-10-18 1949-06-21 Burrough Joe Internal-combustion engine
CH457070A (de) * 1965-11-19 1968-05-31 Polyprodukte Ag Rotierender Antrieb
DE2623234A1 (de) * 1976-05-24 1977-12-01 Alberto Kling Elektromagnetische antriebsvorrichtung
DE3038673A1 (de) * 1980-10-14 1982-05-27 Wilfried 3176 Meinersen Schwant Antriebsmaschine, inbesondere brennkraftmaschine mit kurbelwellenfreier kraftuebertragung und schlitzgesteuertem ladungswechsel
FR2510181A1 (fr) * 1981-07-21 1983-01-28 Bertin & Cie Convertisseur d'energie thermique en energie electrique a moteur stirling et generateur electrique integre

Also Published As

Publication number Publication date
ES2048328T3 (es) 1994-03-16
ATE97991T1 (de) 1993-12-15
GB2226612A (en) 1990-07-04
ES2048327T3 (es) 1994-03-16
DE3773724D1 (de) 1991-11-21
EP0369990B1 (fr) 1993-12-01
WO1987005964A1 (fr) 1987-10-08
EP0369991A1 (fr) 1990-05-23
ATE97992T1 (de) 1993-12-15
EP0240467A1 (fr) 1987-10-07
GB8928577D0 (en) 1990-02-21
JPH0794801B2 (ja) 1995-10-11
JPS63502916A (ja) 1988-10-27
GB2198788B (en) 1990-12-05
ATE68556T1 (de) 1991-11-15
GB8728277D0 (en) 1988-01-13
CA1308155C (fr) 1992-09-29
GB2226710B (en) 1990-12-05
GB2226710A (en) 1990-07-04
EP0369990A1 (fr) 1990-05-23
EP0369991B1 (fr) 1993-12-01
ES2026942T3 (es) 1992-05-16
GB2198788A (en) 1988-06-22
KR880701314A (ko) 1988-07-26
AU7209387A (en) 1987-10-20
DE3788357D1 (de) 1994-01-13
GB2226612B (en) 1990-12-05
KR960000436B1 (ko) 1996-01-06
GB8928578D0 (en) 1990-02-21
KR960000435B1 (ko) 1996-01-06
DE3788358D1 (de) 1994-01-13

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