WO1986006786A1 - Machine a pistons rotatifs - Google Patents

Machine a pistons rotatifs Download PDF

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Publication number
WO1986006786A1
WO1986006786A1 PCT/EP1986/000271 EP8600271W WO8606786A1 WO 1986006786 A1 WO1986006786 A1 WO 1986006786A1 EP 8600271 W EP8600271 W EP 8600271W WO 8606786 A1 WO8606786 A1 WO 8606786A1
Authority
WO
WIPO (PCT)
Prior art keywords
pistons
rotary piston
housing
working medium
passage openings
Prior art date
Application number
PCT/EP1986/000271
Other languages
German (de)
English (en)
Inventor
Hartwig Groeneveld
Hans Soltess
Original Assignee
Hartwig Groeneveld
Hans Soltess
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 Hartwig Groeneveld, Hans Soltess filed Critical Hartwig Groeneveld
Priority to DE8686903315T priority Critical patent/DE3677221D1/de
Priority to AT86903315T priority patent/ATE60404T1/de
Publication of WO1986006786A1 publication Critical patent/WO1986006786A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C1/00—Rotary-piston machines or engines
    • F01C1/02—Rotary-piston machines or engines of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F01C1/063—Rotary-piston machines or engines of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents with coaxially-mounted members having continuously-changing circumferential spacing between them
    • F01C1/073—Rotary-piston machines or engines of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents with coaxially-mounted members having continuously-changing circumferential spacing between them having pawl-and-ratchet type drive
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C1/00—Rotary-piston machines or engines
    • F01C1/02—Rotary-piston machines or engines of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F01C1/063—Rotary-piston machines or engines of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents with coaxially-mounted members having continuously-changing circumferential spacing between them

Definitions

  • the invention relates to a rotary piston machine with at least two side by side rotatable independently of one another about the same longitudinal axis. mounted in preferably only one direction rotatable support disks, which are provided on their radially outer sides at regular intervals with pistons, the pistons on each of the two disks have the same cross-sections and alternately a piston of the one disc and a piston of the other disc in the protrude the same rotationally symmetrical cavity of a housing arranged coaxially to the longitudinal axis.
  • crank drive is required in each of these machines to convert the reciprocating motion into a rotary motion.
  • the crank mechanism makes machines with piston movement relatively complex and heavy.
  • a rotary piston internal combustion engine which works on the principle of the four-stroke gasoline engine and has controlled intake and exhaust valves.
  • the in an annulus of Circular cross-section piston pairs move alternately in cycles by a certain angle of rotation, so that the four cycles of suction-compress-expand-eject are carried out on the front or rear of each piston in succession by increasing and decreasing the distance to the preceding or following piston.
  • Clock feed, piston width, position of the valves and the spark plugs arranged centrally between them are so matched that three rotationally symmetrically arranged valve groups and spark plugs are required for each pair of pistons.
  • a valve group consists of an inlet and an outlet valve, which are installed opposite each other in the wall of the annular space parallel to the axis of rotation of the engine. From Fig. 2 of DE-PS 582 181 it can be seen that the annular space has only a very small proportion compared to the total volume of the internal combustion engine.
  • Rotary piston machines which only have rotating parts are also known. Closed working rooms with rigid walls, at least one of which is moved in such a way that a variable volume of the working room results, are characteristic of rotary piston machines.
  • the variable volume is formed between a power section and a shut-off section.
  • the rotary piston engine contains a stationary shut-off part and a power part which moves with its center of gravity on a circle and additionally rotates around a center of gravity.
  • the piston of the rotary piston engine has the shape of a triangle with convex sides, in which there is an internal toothing on one side which meshes with a fixed gear. The sealing of the work rooms is difficult with the rotary piston engine.
  • the invention is based on the object of developing a rotary piston machine which has a construction which is as simple as possible - -
  • the object is achieved by the measures described in claim 1.
  • the rotary piston machine specified in claim 1 can in principle be used as a power or work machine with appropriate adaptation to the respective working medium. Only a few components are required.
  • the rotary piston machine according to claim 1 is therefore versatile and inexpensive to manufacture.
  • the disks are preferably only rotatable in one direction. Between two adjacent pistons, the piston movements create working spaces with variable volumes. If the disks can only rotate in one direction, depending on the type of rotary piston machine as a power or working machine, a torque is delivered or received in this direction of rotation. A stopping device or the like can be used to block the rotation of the disks in one direction.
  • An inevitable mutual braking or acceleration of the two disks of a rotary piston machine is achieved, for example, by gear transmissions, chain transmissions, belt transmissions, lever transmissions and / or cam disks, wherein the above-mentioned transmission types can also be combined with one another.
  • At least the radially outward-facing sides of the piston heads are expediently adapted to the shape of the inner side of the cavity adjoining them. Only very small clearances are therefore required between the pistons and the inside of the cavity, which can be sealed well by appropriately shaped seals that can be inserted in the grooves of the pistons.
  • the disks are at a small distance from each other on one side of the plane of symmetry with the pistons running through the center of the pistons perpendicular to the longitudinal axis connected. There is preferably a seal between the disks.
  • the sealing of the working chambers between the panes is therefore relatively simple and easy.
  • the housing is arranged at a short distance from the pane walls. It is therefore also possible to insert a seal in the grooves of the panes and / or the walls in order to seal the work spaces at these points.
  • a favorable adaptation to the flow of the working medium is achieved if the front and the rear surface of the piston are designed to be inclined with respect to the longitudinal axis of the rotary piston machine.
  • pairs of passage openings one of which is provided for the supply and one for the discharge of the working medium, at regular intervals with respect to the passage openings intended for the same function along the cavity.
  • the passage openings are designed in the manner of slots and can be closed and released in each case by the pistons and / or support disks.
  • the change in the working medium is controlled via the pistons and / or support disks themselves. It is also possible to arrange the passage openings in the cylindrical outer wall.
  • a preferred embodiment is designed such that the passage openings provided for the supply or for the discharge of the working medium are each arranged in the opposite side walls.
  • the passage openings serving for the supply or discharge of the working medium are each connected to a fresh gas or exhaust gas duct running through 360 ° in the housing.
  • the number of pairs of passage openings and the number of ignition points are expediently the same, this number corresponding to half the number of pistons in the case of an internal combustion engine operating analogously to the two-stroke method or a quarter of the number of pistons in the case of the internal combustion engine operating analogously to the four-stroke method.
  • a number of spark plugs corresponding to the number of pairs of passage openings is arranged at regular intervals along the cavity, a fuel-air mixture being able to be fed into the cavity through the passage openings and being supplied with ignition voltages as a function of the rotational positions of the disks Spark plugs are ignitable.
  • This device works as a gasoline engine. It is also possible to feed air under pressure through the passage openings for the supply of the working medium, and to compress the air so high that fuel injected at the ignition point ignites itself. Such a device works as a diesel engine.
  • the ignition pressure controls a locking device which releases the leading pistons in the direction of rotation at the moment of ignition and connects the trailing pistons to the housing against the direction of rotation.
  • the trailing piston is advantageously brought close to the leading piston and the passage opening serving the supply of the working medium is only released when a minimum piston distance is reached.
  • the pistons can have different shapes. For example, piston pairs can also be used.
  • a rotary piston internal combustion engine with a minimum of moving parts represents the advantageous embodiment with only two pistons, the pistons extending over an angular range of preferably 90 °.
  • a plurality of seals can be arranged on the wide pistons, so that such a rotary piston internal combustion engine has a particularly robust operating behavior and requires no extreme accuracy with regard to the manufacturing tolerances.
  • a rotary piston internal combustion engine with a small diameter
  • favorable cross sections are achieved at the mounting location of a piston if only one piston or one piston group is connected to the inner shaft and the second piston or the second piston group is connected to a rotating intermediate housing .
  • the outer circumference of the cylindrical intermediate housing can be designed as an inner ring of a rolling bearing.
  • Fig. 1 a rotary piston machine in longitudinal section
  • Fig. 2 shows a section along the lines I-I of the rotary piston machine shown in FIG. 1,
  • FIG. 3 schematically shows a rotary piston machine in cross section with through openings, - 7 -
  • FIG. 4 shows a longitudinal section through half of another embodiment of a rotary piston machine
  • FIG. 5 schematically shows a rotary piston machine in cross-section with passage openings arranged in a housing side
  • FIG. 6 schematically shows a rotary piston machine in cross section with a different distribution of the passage openings in the housing
  • Fig. 11 schematically shows the arrangement of flaps in the passage openings for the supply or discharge of the working medium
  • Fig. 15 a to 15 d schematically shows a working with two pistons
  • 16 schematically shows in cross section a rotary piston internal combustion engine with two pistons and a rotating intermediate housing.
  • a rotary piston machine 1 shown in FIGS. 1 and 2 contains a shaft 2 which is rotatably mounted in a housing 3 by means of bearings, not shown. Inside the hollow housing 3, two disks 4, 5 are rotatably mounted on the shaft 2. The disks 4, 5 are next to each other at a short distance. They are independent of each other
  • the disks 4, 5 are each connected to pistons at regular intervals along the circumference.
  • the disc 4 carries z. B. four pistons 8, 9, 10 and 11, while the disc 5 has four pistons 12, 13, 14 and 15.
  • the pistons 8 to 15 have the same cross sections.
  • the cavity 16 is adapted with its side adjacent to the pistons 8 to 15 to the cross-sectional shape of the pistons 8 to 15. Since the disks 4, 5 each merge tangentially with their circular surfaces facing away from one another into the pistons 8 to 15, the side of the cavity facing the pistons 8 to 15 has
  • the disks 4, 5 are arranged at a short distance from each other on one side of the symeetry plane, designated 17 in FIG. 1, which runs through the center of the pistons 8 to 15 and perpendicular to the longitudinal axis 6.
  • passage openings 19, 20 are each arranged for the discharge and supply of liquid and / or gaseous working media.
  • the passage openings 19, 20 are in pairs at equal distances from one another
  • the number of pairs of passage openings 19, 20 corresponds to that - 9 -
  • the embodiment shown in Fig. 4 which is shown in section between two pistons, has a plurality of pistons 21, which have a rectangular cross section with rounded edges.
  • Two disks 22, 23, which are arranged next to one another and are rotatably mounted on the shaft 2 independently of one another, surround at their fastening points with the pistons 21 half of these on their sides facing the shaft 2 and completely on the sides perpendicular to the shaft 2 .
  • the disks 22, 23 therefore already partially form a cover for the pistons 21.
  • passage openings 25, 26 are arranged, which are located in mutually opposite sides 27, 28 of the housing 24.
  • the passage openings 25 are intended for the supply of the working medium and the passage openings 26 for the discharge of the working medium.
  • the disks 22, 23 there are respective passage openings 29, 30 corresponding to the passage openings 25 and 26.
  • the seals are arranged somewhat differently.
  • the pistons 8, 9, 10 and 11 can be moved relative to the pistons 12, 13, 14, 15. In the case of a relative movement with different speeds, 3 working spaces occur in the cavity 16 of the housing, which narrow and widen.
  • the relative movement takes place, for example, in such a way that in each case one disc is completely or almost stationary, while the other disc is about the free path between two pistons 8, 12; 9, 13; 10, 14 and 11, 15 continues to rotate. Then the order of movement of the two disks is reversed.
  • the two disks 4, 5 are each provided with a holding device so that they can only rotate in one direction, which is indicated by the arrow 31 in FIG. 2.
  • a freewheel construction can also be used as a backstop.
  • the device described above can in principle be used as a force and as a working machine.
  • the device can be used as an internal combustion engine, as a pump or as a compressor.
  • the device can be used as an internal combustion engine, as a pump or as a compressor.
  • FIG. 2 shows an embodiment in which 16 spark plugs 32 are provided at regular intervals along the cavity.
  • the device according to FIG. 2 also contains at least one injection valve (not shown in more detail). about
  • the injection valves or inlet channels is in each case at a certain distance between the pistons 8, 12; 9, 13; 10, 14 and 11, 15 an ignitable fuel-air mixture is supplied to the cavity 16, if necessary under pressure.
  • This ignitable mixture is located in the working chambers between pairs of pistons 8, 12; 9, 13; 10, 14 and 11, 15.
  • the disc 5 which has previously been set in rotation remains, while the disc 4 is rotated via the pistons 8, 9, 10, 11 by the expansion of the hot gases.
  • Both discs 4, 5 stand.
  • the pistons 8, 9, 10, 11 of the disc 4 (see FIG. 2), which protrude in the direction of rotation, move by expansion after the ignition has been initiated, while disc 5 with the pistons 12, 13, 14, 15 is stopped at the same time. (Briefly) Before reaching the position in which the latter pistons remain (Fig. 2), disc 5 is loosened, both discs 4 and 5 now move in the direction of rotation until z. B. piston 13 has assumed the position of the piston 9 (shown in FIG. 2).
  • the stop device itself can be designed to be positive or non-positive; in the former case z. B. by a claw-like ring which is arranged laterally in the housing 3 in the (for example) part 18 (or in mirror image with respect to 17 for the other disk) and moves coaxially with the shaft 2 into the disk 5 (for part 18) (or in disk 4 for the mirror-image arrangement) engages.
  • This ring can be designed accordingly.
  • B. be operated electromagnetically (possibly against spring force).
  • the recesses in the disks must be designed such that the two stopping positions per disk and quarter turn z. B. are possible. - -
  • the frictional stopping device could, for. B. be designed so that a brake disc to the respective disc 4 or 5 z. B. is pressed hydraulically.
  • the two stops could not be allowed to occur, but e.g. B. after ignition with the disc 5 standing, the disc 4 can only be turned so far that, for. B. the piston 8 only moves into position 101 (see FIG. 2). Then a further spark plug 102 would have to be arranged, i. H. that a spark plug would have to be provided at intervals of slightly more than 10 mm wide, or that the candle be installed in the piston.
  • the number of pairs of passage openings corresponds to the number of working chambers, which is equal to half the number of pistons.
  • the passage openings 19 for the discharge of the combustion gases may have a further radial distance from the longitudinal axis than the passage openings 20 for the supply of the fuel-air mixture.
  • the Fig. 5 shows an embodiment of a rotary piston engine in which the passage openings 20 for the supply of the fuel-air mixture are designed in the same way as in the device shown in FIG. 3. For the discharge of the hot combustion gases, according to that in FIG. 5
  • FIG. 6 shows an embodiment of a rotary piston engine in which each disk carries only one pair of pistons 35, 36 and 37, 38, respectively. Accordingly, there are only two passage openings 40 for the supply of the working medium and two passage openings 39 for the discharge of the working medium.
  • the passage openings 39, 40 are each around
  • the passage openings for the supply and discharge of the working medium can contain circular sections formed as valve seats in the housing 3.
  • the circular sections are expediently designed as valve seats for valves, not shown, whose opening and closing positions can be controlled as a function of the rotational position via connections to the disks 4, 5 and 22, 23.
  • the spark plugs can expediently be arranged in the pistons instead of in the housing 3.
  • a corresponding arrangement is shown in FIG. 6.
  • the pistons 35 and 36 contain recesses (not shown in more detail) with their side surfaces running perpendicular to the direction of rotation. Spark plugs 41 are arranged in these bulges, which are supplied with ignition voltage via the disk belonging to the pistons 35, 36.
  • Such an arrangement has the advantage that the ignitions do not always have to take place in exactly the same places with respect to the housing 3.
  • the injection nozzles can also be provided in the pistons.
  • the backstop or the holding device for the disks 4, 5 or 22, 23 preferably has a support option for the respective disk held in the rest position.
  • This support device is expediently controlled in connection with the ignition voltage in such a way that the support is activated before the ignition.
  • an exhaust duct extending over an arc of 360 ° can be provided with individual shut-offs.
  • the barriers are matched to the respective positions of the pistons during ignition and the subsequent expansion phase.
  • the in the Fig. 1 to 6 shown rotary piston machines can be connected in parallel, ie several such rotary piston machines can be arranged on a common shaft. - 14 -
  • rotary piston machines are designed as motors that work more frequently in part-load operation, it is possible not to carry out all possible ignitions with several pistons per disk.
  • FIG. 7a to 7d show different embodiments of pistons.
  • semicircular pistons 42 are fastened to a disk 43.
  • a piston 44 is shown, which is approximately rectangular and extends from a disc 45.
  • a double piston 47 is attached to a disk 46.
  • 7d shows another embodiment of a double piston 48.
  • FIG. 7e shows a vertical view of a piston, each with a flat front and rear side, which is embodied axially parallel.
  • FIG. 7f shows a piston with end faces that run obliquely to the axis of rotation, the planes of which do not necessarily have to run at the same angle to the axis of rotation.
  • FIG. 7g shows a piston with a nose-shaped profile, as is advantageously used, for example, in a rotary piston internal combustion engine operating analogously to the two-stroke method.
  • FIG. 7h shows a piston with a combustion chamber let in on one side to achieve a high compression ratio.
  • the torque output is to be illustrated with reference to FIGS. 8 and 9.
  • torque delivery e.g. B. when operating with torque output on both sides.
  • the shaft 2 (see Fig. 8) is divided into 2a and 2b. Storage can take place in one another (but need not be).
  • the disc 4 is firmly connected to shaft 2a, the disc 5 is fixed to 2b. Both shafts each work on a flywheel 105 (or a flange or the like).
  • the transmission in only one direction of rotation takes place by installing z. B. a freewheel 106. Exactly as previously explained for the left side with disk 4, the right side also works in mirror image with disk 5, - 15 -
  • the shaft 102a is designed as a hollow shaft and is firmly connected to the disk 4.
  • the shaft 102b fixedly connected to the disk 5 runs through the shaft 102a.
  • Both shaft ends 102a and 102b are each connected to a flywheel 109 via their own freewheels 107 and 108, respectively. It is also possible according to the invention to connect shaft 102b and hollow shaft 102a to two different flywheels 109a and 109b.
  • Fig. 11 is the arrangement of flaps 19 'and 20' in the passage openings for the discharge line 19 and the supply 20 of the working medium.
  • a locking and release device for the alternate release of the two disks 4 and 5 is shown in Fig. 12.
  • a disk 110 acted upon by the ignition pressure lifts the ends of the two levers 112 and 122, respectively.
  • the lever 112 which is supported at the pivot point 114, lifts a locking member 118 out of a recess in the disk 4 via a pulling device 116.
  • the lever 122 mounted in the fulcrum 124 presses a locking member 128 into a recess in the disk 5 via a plunger 126 during operation.
  • the inner shaft 2 is rotatably mounted with a bearing 130 directly in the housing 3 and is supported on the opposite side by a bearing 136 in the hollow shaft 2a, which is concentrically surrounded by a bearing 132 arranged in the housing 3. On the opposite side, the hollow shaft 2a is supported by a bearing 134 on the inner shaft 2.
  • the washers 4
  • the hollow shaft 2a is sealed on the end face with respect to the disk 5 by means of the annular sealing element 142.
  • the disks 4 and 5 are sealed by means of the likewise annular sealing elements 144 and 146 against the housing and the bearings located therein.
  • the pistons shown here as rectangular in section here carry sealing elements 148 which are arranged towards the outer wall of the housing and towards the opposite disk, in the example shown opposite disk 5.
  • Fig. 14 shows a rotary piston machine with two pairs of pistons working analogously to the four-stroke method, FIGS. 14a-14d representing different phases of the work flow.
  • the pistons 208 and 210 fastened diametrically opposite one another on the same disk and the pistons 212 and 214 fastened on the other disk are rotatably mounted counterclockwise.
  • Reference number 232 designates the spark plug.
  • the center point for the following angle information represents the reference point 0 °.
  • the spark plug opposite is in the angular range of 150 ° - 160 ° the passage opening 219 for the discharge of the working medium and in the angular range of 175 ° - 200 ° the passage opening 220 for the supply of the working medium. Since the piston front and rear sides each delimit different working spaces, the function of the rotary piston internal combustion engine is described below.
  • the mixture is compressed and ignited.
  • a piston is driven on the rear and pushes on its front the mixture burned in the previous cycle through the passage opening 219 to discharge the working medium.
  • the pistons are closest to each other, the transition from the exhaust to the intake stroke taking place.
  • a piston compresses the fresh mixture on its front and sucks in new mixture on its rear.
  • the two shafts each of which is connected to a pair of pistons, are coupled to one another via a gearbox in such a way that one pair of pistons covers the angular ranges 201 and 203, i.e. 30 ° in the same time as the other pair of pistons the angular ranges 202 and 204, i.e. 150 °.
  • the speed ratio is therefore 1: 5.
  • a corresponding switchover takes place at the transitions from one angular range to the next.
  • Fig. 14b shows the piston pair 208/210 offset by 75 ° and the piston pair 212/214 offset by 15 ° compared to FIG. 14a. After a further rotation by 75 ° or 15 ° again, the state shown in FIG. 14c is reached.
  • FIG. 14d A subsequent rotation of the pair of pistons 212/214 by 90 ° and a corresponding rotation of the pair of pistons 208/210 by 18 ° is shown in FIG. 14d.
  • 15a to 15e show the movement sequence of a two-piston rotary piston internal combustion engine in different phases.
  • the two schematically illustrated pistons 301 and 302 each extend over an angular range of 90 °. Movement phases are shown, between which the leading piston has passed through an angular range of 165 ° and the trailing piston has passed through an angular range of 15 °.
  • 15a shows the pistons 301 and 302 rotating counterclockwise at the moment of compression of the working medium in the working space 311. After ignition by means of spark plug 310, the piston 301 moves to the position shown in FIG. 15b, the piston 301 releasing the exhaust gas channel 319 , so that this is connected to the work space 311.
  • the lagging piston 302 reduces the working space 311 and drives the exhaust gas out, as in FIG. 15c is shown.
  • the rear edge of the piston 301 then releases the fresh gas channel 320, from which fresh working medium is sucked into the enlarging working space 311 when the piston 301 is leading, until the one shown in FIG. 15d phase shown is reached.
  • the working medium is now compressed until the starting position known from FIG. 15a shown in FIG. 15a is reached again and the interplay begins again.
  • 16 schematically shows a rotary piston internal combustion engine with two pistons 404 and 406, one piston 406 of which is connected to a rotating cylindrical intermediate housing 405, while the second
  • the piston 406 has a seal 409 on its side facing the holder 410
  • the piston 404 has a seal 408 on its outside facing the intermediate housing 405.
  • the intermediate housing is designed as an inner ring of a roller bearing, which is mounted in the housing 403 by means of a plurality of roller bodies 407.
  • This embodiment is advantageously chosen for rotary piston internal combustion engines with a small diameter. According to the invention, this type of construction is not limited to rotary piston internal combustion engines with two pistons, but a plurality of pistons can also be connected to the holder 410 or the intermediate housing 405, respectively.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Combustion Methods Of Internal-Combustion Engines (AREA)
  • Ignition Installations For Internal Combustion Engines (AREA)
  • Rotary Pumps (AREA)

Abstract

Machine à pistons rotatifs comportant deux disques support rotatifs indépendants l'un de l'autre et pourvus de pistons, dans laquelle respectivement en alternance un piston du premier disque et un piston du second disque font saillie dans la même cavité à symétrie de révolution d'un logement, disposée coaxialement par rapport à l'axe longitudinal afin de réaliser une machine à pistons rotatifs d'une construction aussi simple que possible et possédant un espace accessible au milieu de travail relativement grand par rapport au volume total du logement des pistons, l'espace de travail recevant les pistons s'étend depuis les arbres primaires jusqu'à la paroi du logement, et les pistons et/ou les disques support commandent des orifices de passage ménagés dans les parois du logement pour l'amenée et l'évacuation des milieux de travail. Un moteur à combustion interne de ce type peut être utilisé de manière analogue avec un cycle à deux ou quatre temps et être actionné par un allumage commandé ou un auto-allumage.
PCT/EP1986/000271 1985-05-08 1986-05-09 Machine a pistons rotatifs WO1986006786A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
DE8686903315T DE3677221D1 (de) 1985-05-08 1986-05-09 Rotationskolbenmaschine.
AT86903315T ATE60404T1 (de) 1985-05-08 1986-05-09 Rotationskolbenmaschine.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DEP3516578.2 1985-05-08
DE3516578 1985-05-08

Publications (1)

Publication Number Publication Date
WO1986006786A1 true WO1986006786A1 (fr) 1986-11-20

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Family Applications (1)

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PCT/EP1986/000271 WO1986006786A1 (fr) 1985-05-08 1986-05-09 Machine a pistons rotatifs

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EP (1) EP0259328B1 (fr)
AU (1) AU5901386A (fr)
DE (2) DE3677221D1 (fr)
WO (1) WO1986006786A1 (fr)

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0556563A2 (fr) * 1992-01-25 1993-08-25 Biczuja, Anatolij Moteur à combustion interne
DE4324997A1 (de) * 1993-07-26 1995-02-16 Sabet Huschang Mittelachsige Umlaufkolben-Brennkraftmaschine
FR2778945A1 (fr) * 1998-05-25 1999-11-26 Alfred Lang Moteur circulaire a pistons oscillants
US6257196B1 (en) * 1999-09-07 2001-07-10 Alfredo Alvarado Rotary disc engine
WO2002046580A1 (fr) * 2000-12-08 2002-06-13 Esko Raikamo Unite de puissance commandee par pression
GR1005322B (el) * 2005-04-20 2006-10-18 Παναγιωτης Βασιλειου Ζαραφωνιτης Τοροειδης ερμητικος κινητηρας
US7222601B1 (en) * 2005-07-08 2007-05-29 Kamen George Kamenov Rotary valveless internal combustion engine
US7631632B2 (en) * 2003-11-21 2009-12-15 Anatoly Arov Orbital engine/pump with multiple toroidal cylinders
US20170044899A1 (en) * 2015-03-12 2017-02-16 Edward Alan Hicks Motor/engine with rotating pistons
WO2022187920A1 (fr) * 2021-03-07 2022-09-15 Oliveira Luciano Barros Système de pompage à spirales internes

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FR2206789A5 (fr) * 1972-11-10 1974-06-07 Gudin Michel
DE2321348A1 (de) * 1973-04-27 1974-11-07 Udo Dr Ing Ohrt Doppeldrehkolbenmotor - verbrennungskraftmaschine mit innerer verbrennung
DE2437714A1 (de) * 1974-08-06 1976-03-04 Deutsche Forsch Luft Raumfahrt Schlitzsteuerung des gaswechsels bei der schwingdrehkolbenmaschine

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US1458641A (en) * 1921-02-28 1923-06-12 Cizek Vojtech Rotary internal-combustion engine
CH110173A (de) * 1924-08-07 1925-05-16 Guetlin Willy Ventillose Verbrennungskraftmaschine.
FR688097A (fr) * 1929-10-29 1930-08-19 Moteur rotatif à explosions à turbine centrale
US2362550A (en) * 1943-10-11 1944-11-14 Carl B Hansen Rotary engine
US3112062A (en) * 1960-08-19 1963-11-26 David G Way Rotary pumps and engines
US3087671A (en) * 1961-06-16 1963-04-30 George A Myles Rotary engines, pumps, and compressors
US3282258A (en) * 1964-08-06 1966-11-01 Edmond L Sinnott Rotary engine
US3550563A (en) * 1969-04-02 1970-12-29 Thomas Albert Smith Rotary engine
BE776588A (fr) * 1971-12-13 1972-04-04 Delahaut Marcel R Moteur a explosion a quatre temps, rotatif et sans soupapes.
FR2206789A5 (fr) * 1972-11-10 1974-06-07 Gudin Michel
DE2321348A1 (de) * 1973-04-27 1974-11-07 Udo Dr Ing Ohrt Doppeldrehkolbenmotor - verbrennungskraftmaschine mit innerer verbrennung
DE2437714A1 (de) * 1974-08-06 1976-03-04 Deutsche Forsch Luft Raumfahrt Schlitzsteuerung des gaswechsels bei der schwingdrehkolbenmaschine

Cited By (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0556563A2 (fr) * 1992-01-25 1993-08-25 Biczuja, Anatolij Moteur à combustion interne
EP0556563A3 (en) * 1992-01-25 1993-12-01 Biczuja Anatolij Internal combustion engine
DE4324997A1 (de) * 1993-07-26 1995-02-16 Sabet Huschang Mittelachsige Umlaufkolben-Brennkraftmaschine
US5722361A (en) * 1993-07-26 1998-03-03 Huschang Sabet Internal combustion engine with pistons that rotate about a center line
FR2778945A1 (fr) * 1998-05-25 1999-11-26 Alfred Lang Moteur circulaire a pistons oscillants
US6257196B1 (en) * 1999-09-07 2001-07-10 Alfredo Alvarado Rotary disc engine
WO2002046580A1 (fr) * 2000-12-08 2002-06-13 Esko Raikamo Unite de puissance commandee par pression
US7631632B2 (en) * 2003-11-21 2009-12-15 Anatoly Arov Orbital engine/pump with multiple toroidal cylinders
GR1005322B (el) * 2005-04-20 2006-10-18 Παναγιωτης Βασιλειου Ζαραφωνιτης Τοροειδης ερμητικος κινητηρας
US7222601B1 (en) * 2005-07-08 2007-05-29 Kamen George Kamenov Rotary valveless internal combustion engine
US7931006B1 (en) * 2005-07-08 2011-04-26 Kamen George Kamenov Valveless rotary internal combustion engine
US20170044899A1 (en) * 2015-03-12 2017-02-16 Edward Alan Hicks Motor/engine with rotating pistons
US9719350B2 (en) * 2015-03-12 2017-08-01 Edward Alan Hicks Motor/engine with rotating pistons
WO2022187920A1 (fr) * 2021-03-07 2022-09-15 Oliveira Luciano Barros Système de pompage à spirales internes

Also Published As

Publication number Publication date
EP0259328A1 (fr) 1988-03-16
DE3677221D1 (de) 1991-02-28
EP0259328B1 (fr) 1991-01-23
AU5901386A (en) 1986-12-04
DE3690232D2 (en) 1988-06-01

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