EP2032801A1 - Moteur a pistons alternatifs rotatifs - Google Patents

Moteur a pistons alternatifs rotatifs

Info

Publication number
EP2032801A1
EP2032801A1 EP05825337A EP05825337A EP2032801A1 EP 2032801 A1 EP2032801 A1 EP 2032801A1 EP 05825337 A EP05825337 A EP 05825337A EP 05825337 A EP05825337 A EP 05825337A EP 2032801 A1 EP2032801 A1 EP 2032801A1
Authority
EP
European Patent Office
Prior art keywords
rotor
machine according
piston
housing
reciprocating
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP05825337A
Other languages
German (de)
English (en)
Inventor
Hans-Gerd RÜCKER
Rainer Guder
Ralf Georg Lipiensky
Manfred THÖNNESSEN
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Dezmotec AG
Original Assignee
Dezmotec AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Dezmotec AG filed Critical Dezmotec AG
Publication of EP2032801A1 publication Critical patent/EP2032801A1/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • 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
    • 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
    • F01B9/00—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups
    • F01B9/04—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups with rotary main shaft other than crankshaft
    • F01B9/06—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups with rotary main shaft other than crankshaft the piston motion being transmitted by curved surfaces
    • 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
    • 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
    • F01B9/00—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups
    • F01B9/04—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups with rotary main shaft other than crankshaft
    • F01B9/06—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups with rotary main shaft other than crankshaft the piston motion being transmitted by curved surfaces
    • F01B2009/061—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups with rotary main shaft other than crankshaft the piston motion being transmitted by curved surfaces by cams
    • F01B2009/063—Mono-lobe cams
    • 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
    • F01B9/00—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups
    • F01B9/04—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups with rotary main shaft other than crankshaft
    • F01B9/06—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups with rotary main shaft other than crankshaft the piston motion being transmitted by curved surfaces
    • F01B2009/061—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups with rotary main shaft other than crankshaft the piston motion being transmitted by curved surfaces by cams
    • F01B2009/065—Bi-lobe cams
    • 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
    • F01B9/00—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups
    • F01B9/04—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups with rotary main shaft other than crankshaft
    • F01B9/06—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups with rotary main shaft other than crankshaft the piston motion being transmitted by curved surfaces
    • F01B2009/061—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups with rotary main shaft other than crankshaft the piston motion being transmitted by curved surfaces by cams
    • F01B2009/066—Tri-lobe cams
    • 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
    • F01B9/00—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups
    • F01B9/04—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups with rotary main shaft other than crankshaft
    • F01B9/06—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups with rotary main shaft other than crankshaft the piston motion being transmitted by curved surfaces
    • F01B2009/061—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups with rotary main shaft other than crankshaft the piston motion being transmitted by curved surfaces by cams
    • F01B2009/068—Quadri-lobe cams

Definitions

  • the invention relates to a reciprocating piston machine and in particular to a rotary reciprocating piston machine which can be used both as a working machine and also as an internal combustion engine, in particular as a four-stroke internal combustion engine.
  • the conventional reciprocating piston machine In conventional reciprocating piston machines, the power is transmitted from the pistons to a crankshaft via connecting rods. Exhaust valves and intake valves are provided in the cylinder head and are controlled by the crankshaft via one or more camshafts.
  • the conventional reciprocating piston machine has relatively large dimensions and is assembled from a large number of different individual parts. Conventional motors have great difficulty running reliably with biofuels over a long period of time, since biofuels always contain a certain amount of foreign substances that are very difficult to filter out. In the engine compartment, the intake and exhaust valves and everything related to the valves are primarily affected. They stick together after a very short time and can no longer be controlled, the result of which is that the motor must be cleaned.
  • the object of the invention is to provide a reciprocating piston machine which has a compact, simple and lightweight construction with relatively few individual parts and wherein no inlet and outlet valves are required.
  • the invention provides a reciprocating piston machine according to independent claim 1.
  • the reciprocating piston machine can also be operated with biogas for longer periods before being cleaned or serviced.
  • the construction of the reciprocating piston machine according to the invention enables simple assembly and maintenance. Since there are no valves with the associated valve control, there is also less noise. With regard to saved friction losses, an efficiency increase of up to 60% is expected. Since there is no power transmission via connecting rods to a crankshaft, no transverse forces act on the pistons, which means that piston wear is reduced to a minimum and flatter and therefore lighter pistons can be used.
  • the cam tracks fixed to the housing can be designed so that, in the case of an internal combustion engine, the piston runs through one or more, preferably two, working cycles per revolution of the engine, which is a doubling (in one working cycle) or quadrupling (in two working cycles) compared to the conventional four-stroke engine.
  • the engine can run slower and the life of the individual components is increased.
  • the cam tracks can be designed to provide one, two, three, four or more working cycles per revolution.
  • pistons can be arranged at the same distance around the axis of rotation of the piston machine, and this reduces the vibrations of the engine. Thanks to the simple circular shape of the rotor, sealing problems, such as are known with Wankel engines, can largely be ruled out. The higher efficiency leads to lower fuel consumption and reduced emissions. With just a few structural changes, all fuels on the market can be used. Extending the combustion path results in a reduction in NOx emissions.
  • the engine can possibly be operated without a catalytic converter and is particularly suitable for combined heat and power (generator operation).
  • the rotor has a cylindrical rotor body which is provided with a plurality of radial bores which are at the same angular distance from one another in the circumferential direction and their
  • Central axes are located in a common plane which is oriented perpendicular to the axis of rotation of the rotor.
  • the holes extend from the circular
  • Circumferential surface of the rotor are inwards and in the bores
  • Cylinder liners are used in a floating manner, in which the pistons can move radially inwards and outwards.
  • the floating cylinder liners are pressed radially outwards by centrifugal force and possibly also supported by spring means in contact with a circular housing inner wall in order to seal the cylinder chambers tightly against the housing inner wall.
  • the guide means of the sliding pieces preferably consist of axial pins which are provided with a sliding sleeve made of bearing metal or with roller bearings, preferably needle bearings, to reduce friction. On both sides of the
  • Rotors are flanged drive or output shafts which are rotatably mounted in the housing. These waves are preferably hollow and communicate with a medium one
  • Lubricant preferably oil, which is supplied to an oil cooler after exiting the reciprocating piston machine and after
  • Cooling is reintroduced into the piston machine.
  • the housing of the reciprocating piston machine can be air-cooled or water-cooled.
  • the sliders can be guided in radial guides of the rotor body and / or in radial slots of flanges of the drive or output shafts, which are fastened to the end faces of the rotor body.
  • the invention provides a reciprocating piston machine according to independent claim 11.
  • the sliders are eliminated since the transverse shaft itself is guided through the curved tracks.
  • the structural design is thus even simpler and the friction loss of the sliding pieces in the guide grooves is eliminated.
  • the piston rod can be guided in a plain bearing bush or ball bush with low friction.
  • Suction and discharge openings are provided on the housing.
  • fuel and water or steam injection devices can also be provided.
  • Figure 1 is a side view of the rotary reciprocating machine according to the invention.
  • FIG. 2 shows an end view of the rotary reciprocating piston machine according to FIG. 1;
  • Figure 3 is a cross-sectional view of the rotary reciprocating machine along line A-A 'of Figure 2;
  • FIG. 4 shows a cross-sectional view of the rotary piston machine along the line CC in FIG. 1; and FIG. 5 shows a cross-sectional view along the line BB ′ in FIG. 1.
  • Figure 6 is an end view, partially cut away, of the rotor body
  • Figure 7 is an end view of an input or output shaft with a mounting flange
  • Figure 8 shows the piston assembly with piston, piston rod, cross shaft and sliders
  • Figure 9 shows a modified guideway for execution as an internal combustion engine.
  • Figures 10 and 11 other modified cam tracks for execution as a working machine.
  • Figure 12 shows another embodiment of the rotary reciprocating machine.
  • the design of the rotary reciprocating piston machine as a motor or internal combustion engine is described below.
  • the rotary reciprocating piston machine according to the invention can also be used as a pump or compressor or compressor.
  • the rotary reciprocating piston machine is also described below with reference to an exemplary embodiment with three pistons. However, it is pointed out that the machine can also be designed as a single- or two-piston machine or as a machine with four or more than four pistons.
  • the reciprocating piston engine has a housing consisting of an outer cylindrical jacket ring 1, which is closed at both ends by two covers 6a and 6b.
  • the covers 6a and 6b are screwed to the casing ring 1 at the points 1a.
  • Several screw points Ia are spaced apart in the circumferential direction.
  • the cylindrical inner surface of the casing ring 1 is preferably grooved and the casing ring 1 and the covers 6a and 6b can be made of gas-nitrided ST52-3.
  • the housing is attached to a support stand (not shown).
  • a rotor body 2 of a rotor is located in the cavity which is surrounded by the casing ring 1 and is closed at both ends of the casing ring 1 by the covers 6a and 6b.
  • the rotor body 2 has a cylindrical peripheral surface and a radial end face on each of its two sides.
  • the rotor also has a hollow shaft or hollow stub shafts 7 on each side of the rotor body 2.
  • the shafts 7 have support flanges 7a which extend radially outwards from the shafts 7 to the outer circumference of the rotor body 2 and by means of screw bolts (not shown) in the Threads are attached to the rotor body 2.
  • the shafts 7 are supported by the housing via bearing devices.
  • bearing devices each have a bearing housing 9 fastened to the outside of each cover 6, 6a, in which a roller bearing 8 is arranged, which carries the associated shaft 7.
  • the rotor accordingly comprises the rotor body 2, and the support flanges 7a with the shafts or stub shafts 7, which also serve as bearing journals of the rotor.
  • the rotor body 2 has three radial cylinder bores 2a, which are located at an angular distance of 120 °.
  • the bores 2a extend radially inward from the circumferential surface of the rotor body 2 to a bottom surface
  • the bores 2a have radial center lines L, which in lie in a common radial plane, which is perpendicular to a rotation axis A of the rotor and all center lines L intersect at a common intersection S in the radial plane on the rotation axis A.
  • the rotor body 2 also has a central, axial through-hole 2b, which is connected to the hollow shafts 7.
  • each radial grooves 2c are milled into each radial end face of the rotor body 2 and extend in the radial direction parallel to the bore center lines L. These grooves 2c extend from the central bore 2b of the rotor body 2 to its peripheral surface. Accordingly, each cylinder bore 2a lies between two radial grooves 2c and the grooves 2c are parallel to the bore center lines L.
  • the grooves 2d are provided for a purpose which will be described in more detail later.
  • each hole leads from the base 2a '
  • the opening 2d has a smaller diameter than the cylinder bore 2a and serves as one
  • the threaded holes 2e shown in FIGS. 3 and 6 are provided for the screws (not shown) for fastening the shaft flanges 7a to the rotor body 2. These screws protrude through openings 7b in the shaft flanges 7a (see FIG. 7 ).
  • the rotor preferably consists of an aluminum alloy AL-CU-Nl 7-13 and its diameter is preferably about 1 mm smaller than the inside diameter of the cylindrical shell 1.
  • a cylinder liner 3 is floatingly supported in the radial direction.
  • the radially inner end of the cylinder liner 3 is flat and is located in a plane that is perpendicular to the center line L of the associated rotor bore 2a.
  • the cylinder liner 3 is in the form of a circular arc, the radius of the circular arc corresponding to the radius of the inner surface of the outer casing 1 of the housing.
  • the cylinder liners 3 consist of gray cast iron and are coated with gunmetal at their radially outer end.
  • the floating cylinder liners 3 are pressed outwards against the inner surface of the outer shell 1 by centrifugal force during the rotation of the rotor 2.
  • Disc springs 3a can also be arranged between the cylinder liners 3 and the base surface 2a 'of the cylinder bore 2a in order to press the cylinder liners 3 outwards for tight contact with the inner cylindrical surface of the outer casing 1.
  • a piston 4 is slidably received in each cylinder liner 3 and is provided on its circumference with the usual piston rings 4a for sealing against the cylinder liner 3.
  • the pistons 4 are movable in the radial direction outwards and inwards in the cylinder liners 3 and cylinder chambers ZK are enclosed between the outer sides of the pistons 4 and the inner surface of the cylindrical outer casing 1.
  • the pistons 4 can be made of commercially available steel ST 52-3 or Dural, for example.
  • a piston rod 5a is attached to each piston 4 on the side facing away from the cylinder chamber ZK.
  • the piston rod 5a is screwed to the piston 4, the thread allows a fine adjustment of the piston 4 in relation to the piston rod 5a.
  • a lock nut 5b retains the piston 4 in the set position with respect to the piston rod 5a. If the use of this motor is certain from the outset, this type of securing can be dispensed with, as a result of which the setting of the piston 4 with respect to the piston rod 5a is structurally determined.
  • the piston rod 5a extends concentrically to the center line L of the associated rotor bore 2a from the piston 4 inward through the radial opening 2c into the center bore 2b of the rotor body 2 and is provided at its inner end with a bearing eye 5a 'in which an axial or transverse shaft 5c is added, which is parallel over the axial dimension or width of the rotor body 2 extends from one end face thereof to the other end face of the rotor body 2.
  • the transverse shaft 5c carries a sliding piece 5d which extends radially outward from the transverse shaft 5c at each end.
  • the sliders 5d sit in the radial grooves 2c of the rotor 2 and are radially displaceable in these grooves 2c.
  • Each slide 5d has on its outer side, which points away from the piston 4, approximately at its radially outer end, an axial pin 5e which is aligned parallel to the axis of rotation A of the rotor.
  • the pins 5e protrude through radial slots 7c in the flanges 7a and are movable in these slots in the radial direction.
  • each housing cover 6a, 6b On the radial inner surface of each housing cover 6a, 6b, a cam 6 is fastened, which is received between the associated cover 6a or 6b and the flange 7a of the associated shaft 7.
  • the cams 6 are fastened to the covers 6a, 6b by means of bolts 10 which protrude through through holes in the cams 6 and through-holes aligned therewith in the covers 6a and 6b and are screwed into threaded holes in the bearing receptacles 9.
  • Each cam disk 6 is provided on its inner side facing the rotor body 2 with a star-shaped cam track or guide groove 6 ', see in particular FIG. 5, in which the pins 5e of the sliding pieces 5d are received and rotate when the rotor 2 rotates.
  • the sliding or rolling bearings arranged on the pins 5e reduce the friction of the pins 5e in the guide grooves 6 '.
  • cam tracks or guide grooves 6 ' can also be milled directly into the covers 6a, 6b.
  • Cam disks can then be omitted.
  • the cam tracks are stationary or immovable with respect to the housing, ie fixed to the housing, since the covers 6a, 6b are housing parts.
  • the bearing receptacles 9 of the hollow shafts 7 can be included in the construction, so that only positions 6, 6a and 9 or positions 6, 6b and 9 each consist of only one component.
  • each star-shaped guide groove 6 ′ has four curve vertices spaced apart from one another by 90 °, which determine top dead centers of the pistons 4 and, in the circumferential direction, centrally arranged curve vertices between the vertices that determine the bottom dead centers of the pistons 4.
  • the top dead centers are labeled OT1, 0T2, OT3 and OT4 and the bottom dead centers are labeled UT1, UT2, UT3 and UT4.
  • the pistons 4 are alternately controlled inwards and outwards via the pins 5e, the sliding pieces 5d, the transverse shaft 5c and the piston rod 5a in order to carry out the lifting movements.
  • an associated piston 4 is first moved radially inwards to bottom dead center UT1, then again radially outwards to top dead center 0T2, then again radially inwards to bottom dead center UT2, etc.
  • the outer casing 1 of the machine housing has radial inlet openings Id, see FIG. 3, for combustion air or for a fuel-air mixture and radial outlet openings Ib for the combustion gases, as well as threaded bores Ic for spark plugs (not shown) and connections 12, if desired, for injecting water into the Cylinder chambers ZK after ignition and passage through the assigned top dead center.
  • the pistons 4 are again controlled outwards by the interaction of the pins 5e with the guide grooves 6 ′ to expel the combustion gases, then moved inwards to suck in a new charge and finally moved outwards again Compression of the new charge sucked in until a new ignition can take place.
  • the internal combustion engine with rotary reciprocating piston 4 thus works according to the usual four-stroke principle.
  • a curved track 6 '' in the form of an elongated, e.g. approximately kidney-shaped or 8-shaped loop can be provided, as shown in Figure 9.
  • a curved track 6 '' in the form of an elongated, e.g. approximately kidney-shaped or 8-shaped loop
  • Only one working cycle would take place per revolution of the rotor. With larger motors, more than two work cycles per revolution are also possible.
  • FIGS. 10 and 11 When running as a work machine such as other cam tracks can also be provided as a pump for liquid media or a compressor for gaseous media, as shown in FIGS. 10 and 11.
  • 10 is approximately circular and eccentric with respect to the axis of rotation A of the rotor. 10, the piston performs one working cycle per revolution, i.e. a suction stroke and a compression or pumping stroke.
  • the curved path 6 "'of FIG. 10 could also be oval, elliptical or egg-shaped.
  • FIG. 11 shows a star-shaped curved path 6 ′′ ′′ with three arms for three working cycles per rotor revolution the axis A of the pump or compressor rotor.
  • the cam track 6 ′′ according to FIG. 9 can also be used for the execution as a pump or compressor for two working cycles per revolution.
  • the input or output can take place via both or only one of the shafts 7.
  • the sliders 5d can also be guided in the radial slots 7c of the flanges 7a.
  • the sliding pieces 5d could also be guided only in the slots 7c of the flanges 7a and the guides 2c in the rotor body 2 could be dispensed with.
  • the through-bore 2b of the rotor body 2 also have a smaller diameter and could have an axial through-slot (not shown) for each cylinder bore 2a, which extends the rotor bore 2b radially outwards and opens into the cylinder bore 2a.
  • the piston rod 5a would extend into the axial through slot and the transverse shaft 5c would be received in the through slot and movable radially inwards and outwards therein.
  • the flanges 7a can either partially or completely cover the end faces of the rotor body 2.
  • the radial slots in the flange extend to the outer circumference thereof.
  • these radial slots 7c are designed as elongated holes which do not extend to the outer circumference of the flange, see FIG. 7.
  • FIG. 1 A simplified embodiment of the invention is shown in FIG.
  • the axial transverse shaft 5c projects through radial slots 7c 'in the supporting flanges 7a' and is received at the ends in the curved tracks 6 '.
  • the sliders 5d are thus eliminated.
  • Sliding sleeves 5f made of bearing metal or roller bearings, such as, for example, needle bearings, sit on the ends of the transverse shaft 5c 'for low-friction guidance of the transverse shaft 5c' in the curved grooves 6 '.
  • the piston rod 5a is guided in the rotor body 2 'in the radial direction.
  • a bearing bushing or ball bushing (not shown) can also be inserted into the rotor body 2 'for low-friction guidance of the piston rod 5a.
  • the cylinder space under the piston 4 is connected via one or more drilled holes 13 (one shown schematically) to an essentially unpressurized interior of the rotor or the housing, so that no counterpressure can build up below the piston 4.
  • the transverse shaft 5c ' is received in a central axial bore or in axial slots of the rotor body 2'.
  • the cylinder liner 3 is not shown in FIG. 12, but can also be provided.
  • the cam tracks 6 ' are designed as in the first embodiment.

Landscapes

  • 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)
  • Reciprocating Pumps (AREA)
  • Transmission Devices (AREA)
  • Compressor (AREA)

Abstract

L'invention concerne un moteur à pistons alternatifs rotatifs comportant un rotor logé de façon rotative dans un carter, plusieurs pistons pouvant se déplacer radialement dans ledit rotor, entre un point mort extérieur et un point mort intérieur. Chaque piston comporte une tige de piston logée sur un arbre transversal fixé, sur une extrémité, à une pièce de glissement pouvant coulisser dans le rotor, dans des rainures radiales, sur les deux côtés du piston. Les pièces de glissement comportent, sur leur côté extérieur opposé au piston, respectivement un pivot logé dans une rainure de guidage sans fin en forme d'étoile, fixe par rapport au carter. La rainure de guidage s'étend autour d'un axe de rotation du rotor et provoque les mouvements des pistons dans la direction radiale, entre les points morts extérieur et intérieur.
EP05825337A 2005-12-21 2005-12-21 Moteur a pistons alternatifs rotatifs Withdrawn EP2032801A1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/EP2005/057063 WO2007079766A1 (fr) 2005-12-21 2005-12-21 Moteur a pistons alternatifs rotatifs

Publications (1)

Publication Number Publication Date
EP2032801A1 true EP2032801A1 (fr) 2009-03-11

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP05825337A Withdrawn EP2032801A1 (fr) 2005-12-21 2005-12-21 Moteur a pistons alternatifs rotatifs

Country Status (10)

Country Link
US (1) US8316817B2 (fr)
EP (1) EP2032801A1 (fr)
CN (1) CN101371006A (fr)
AR (1) AR058612A1 (fr)
BR (1) BRPI0520762A2 (fr)
CA (1) CA2634854A1 (fr)
IL (1) IL192385A0 (fr)
MX (1) MX2008008133A (fr)
SA (1) SA07280112B1 (fr)
WO (1) WO2007079766A1 (fr)

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CN102913321A (zh) * 2011-08-03 2013-02-06 魏九洲 内摆线旋转活塞内燃机及压缩机
US8931455B2 (en) * 2012-03-23 2015-01-13 Boots Rolf Hughston Rotary engine
US10408201B2 (en) 2015-09-01 2019-09-10 PSC Engineering, LLC Positive displacement pump
ES2698798A1 (es) * 2017-08-04 2019-02-05 Oller Asensio Jose Motor de combustion con bloque giratorio portacilindros
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CN110185536A (zh) * 2019-07-03 2019-08-30 吕国良 转子组、转子内燃机、车辆、飞行器及船舶
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WO2007079766A1 (fr) 2007-07-19
MX2008008133A (es) 2009-01-12
US8316817B2 (en) 2012-11-27
BRPI0520762A2 (pt) 2009-05-26
US20090266316A1 (en) 2009-10-29
CN101371006A (zh) 2009-02-18
CA2634854A1 (fr) 2007-07-19
AR058612A1 (es) 2008-02-13
SA07280112B1 (ar) 2011-06-22
IL192385A0 (en) 2008-12-29

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