EP0011762B1 - Moteur à pistons rotatifs - Google Patents

Moteur à pistons rotatifs Download PDF

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Publication number
EP0011762B1
EP0011762B1 EP79104449A EP79104449A EP0011762B1 EP 0011762 B1 EP0011762 B1 EP 0011762B1 EP 79104449 A EP79104449 A EP 79104449A EP 79104449 A EP79104449 A EP 79104449A EP 0011762 B1 EP0011762 B1 EP 0011762B1
Authority
EP
European Patent Office
Prior art keywords
engine according
rotor
chambers
ring structure
vanes
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.)
Expired
Application number
EP79104449A
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German (de)
English (en)
Other versions
EP0011762A1 (fr
Inventor
Reinhold Gäbler
Jürgen Dr. Dipl.-Ing. Kuechler
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.)
Kuechler Juergen Dr
Original Assignee
Kuechler Juergen Dr
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Publication date
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Priority to AT79104449T priority Critical patent/ATE4065T1/de
Publication of EP0011762A1 publication Critical patent/EP0011762A1/fr
Application granted granted Critical
Publication of EP0011762B1 publication Critical patent/EP0011762B1/fr
Expired legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C1/00—Rotary-piston machines or engines
    • F01C1/30—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F01C1/34—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F01C1/08 or F01C1/22 and relative reciprocation between the co-operating members
    • F01C1/344—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F01C1/08 or F01C1/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
    • F01C1/352—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F01C1/08 or F01C1/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the vanes being pivoted on the axis of the outer member
    • 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
    • F01C11/00—Combinations of two or more machines or engines, each being of rotary-piston or oscillating-piston type
    • F01C11/002—Combinations of two or more machines or engines, each being of rotary-piston or oscillating-piston type of similar working principle
    • F01C11/004—Combinations of two or more machines or engines, each being of rotary-piston or oscillating-piston type of similar working principle and of complementary function, e.g. internal combustion engine with supercharger
    • 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
    • F01C17/00—Arrangements for drive of co-operating members, e.g. for rotary piston and casing
    • F01C17/02—Arrangements for drive of co-operating members, e.g. for rotary piston and casing of toothed-gearing type

Definitions

  • the present invention relates to a rotary piston engine.
  • a machine with a fixed, essentially cylindrical housing which has inlet and outlet openings and in whose end caps a shaft with a rotor is mounted, which consists of two or more hinged disks and forms a number of variable-volume chambers between blades, which seal through a sliding ring of a segment ring surrounding the rotor.
  • the compressed fuel-air mixture can be ignited by means of an ignition device near or in the smallest main compression chamber.
  • the rotary piston machine has abrasive seals and a generally inadequate wing arrangement. It consists of a number of flights, each with a disc on the inner rotor, which always enclose the same angle to the rotor and are only phase-movable by being displaced against one another despite the flat friction of the discs. The torque transmission must take place between the housing, with which one axis is firmly connected, and the rotor shaft; however, the document does not provide any further details on practical implementation.
  • a machine in which a rotary piston arrangement is provided in the stationary housing, which also has an inner rotor made of superimposed ring disks with rigidly attached radial vanes as slides.
  • the outer ring has segments with sliding blocks for guiding the slides, which, with a frictional seal, run around with their ends against the housing wall.
  • Another disadvantage of the known rotary piston engine is that the pre-compression takes place in the inner and the secondary compression in the outer ring chamber system; Although this is not expedient in terms of cooling technology, it must be bought with the serious disadvantage that the volume ratios only allow poor compression and thus a low overall efficiency.
  • the power to weight ratio is also relatively high.
  • Machines according to DE-OS 2 134 565 and 2402 116 have even greater disadvantages, since in the arrangements described there an eccentric shaft or crank is mounted in the stationary housing, the vanes serving to separate the chambers of a rotor radially and back and forth in slot guides emotional.
  • the rotary piston rotating in this way causes a compression similar to a cylinder piston due to its reciprocating movement, even if additional angular movements occur. This mechanism is very prone to failure. The very considerable imbalance of the masses moved back and forth is particularly unfavorable.
  • the object of the invention is seen to improve the known rotary piston machines with simple and economical means so that they are less prone to failure thanks to the clear and inexpensive structure and have a high performance in relation to the weight of the machine and that quiet, smooth running ensures a wide speed range is.
  • the rotary piston machine according to the invention is characterized by the combination of features of claim 1.
  • the production requires a relatively low manufacturing effort.
  • the outer chamber ring system ensures good pre-compression, so that high compression is achieved in the inner main compression chambers. Since both ring arrangements are multi-chamber systems, which come into flow connection via a stationary crescent-shaped passage, several work cycles, some of which overlap, take place per cycle. This ensures in a very simple manner an extremely uniform rotation with constant, at least approximately constant, torque and power output on a common drive connection with output shaft. Because the inner rotor on the one hand and the segment ring surrounding it on the other hand only rotate centrically and both synchronously, the vanes are pivoted in a phase-movable manner with relative translation to the two ring arrangements.
  • the blades which run past the inside wall of the housing without contact, have a fan function in certain circumferential positions of the outer chambers, but in all positions of the inner chambers only a space limiter or compressor function. Thanks to the relatively small mass and partly counter-rotating movement of the vanes, the unbalance generated is very low overall, so that the rotary piston machine according to the invention is characterized by an extremely smooth running.
  • the housing has an inner bearing cover, on which the segment ring is mounted, and an outer plate, which supports the shaft of the rotor. This construction requires only a small amount of space and is therefore very compact and ensures stable storage with the simplest of means.
  • the common drive connection has a double gearwheel which meshes with a gearwheel held on the shaft as well as with another gearwheel at an axial distance from it, which gearwheel is non-rotatably connected to a disk holding the segment ring, preferably on a flange shoulder.
  • the very inexpensive construction can be designed according to the invention in such a way that the double gearwheel is mounted close to the housing circumference and the two gearwheels in engagement with it have the same pitch and the same number of teeth; uniform gears can then be used.
  • a similar gear drive is known from FR-A-1 377 896.
  • this document relates to a positive displacement pump, and the drive connection mentioned there provides a special joint arrangement in order to control the delivery volume.
  • the change in the center distance brings about an increase or decrease in the rotor for the purpose of setting the pump operation between idling and full load.
  • This document does not show any relation to the flow-connected chamber systems rotating in a fixed center distance in an internal combustion engine with filling, compression, ignition, explosion and ejection of a fuel-air or exhaust gas mixture.
  • An air supply device can also be provided on the cover side, for example with an overflow channel, which starts from a circumferential region of the outer chamber-ring arrangement which is approximately diametrically opposite the inlet opening and opens at a circumferential zone on the flange shoulder, the angular position of which is close to that of the inlet opening.
  • the pre-compressed mixture or gas can also be fed directly, for example through a pipeline.
  • the gas mixture sucked in through the inlet or, in the case of injection machines, the air sucked in is thus removed from the peripheral region of the outer chamber-ring arrangement by a flow connection, e.g. B. the overflow channel to the flange approach promoted into the inner chamber-ring arrangement.
  • the crescent-shaped passage opening is stationary with respect to the circumferential chamber-ring arrangements; it is in constant flow connection with a pipe system or with the peripheral region of the mouth of the overflow channel.
  • a particularly rapid, complete filling of the circulating chambers between the two rotating ring arrangements is therefore possible, namely on approximately half a revolution (180 °).
  • the sucked-in gas mixture or, in the case of injection machines, the sucked-in air is thus conveyed from the peripheral region of the outer chamber-ring arrangement through the overflow channel to the flange attachment into the inner chamber-ring arrangement.
  • the circumferential chambers would be charged with precompressed gas or mixture from the crescent-shaped passages, so that the subsequent main compression takes place with high compressions. Ignition takes place in the smallest volume chamber by means of an ignition device during Otto operation; in diesel operation, the compression at the narrowest point of the inner chambers ensures that the mixture ignites automatically.
  • embodiments of the invention provide that the segment ring is sealed off from the rotor, e.g. B. by means of a resilient cover plate, by means of spring tongues arranged in the cover-side circumferential grooves o., Like., And that each sliding block holds two or more spring tongues, which fit snugly on flat surfaces of the associated wing, in particular with different radial distances to the inner end.
  • Spring tongues are preferably arranged in the grooves on the cover side in a manner known per se.
  • the expulsion of the exhaust gas is particularly facilitated in that the wings have a recess at their free outer ends, which forms a radial flow passage when it passes through the associated sliding block.
  • expansion takes place in the subsequently enlarging inner chambers for about a third of a revolution, with a rapid increase in volume under the explosion pressure resulting in favorable gas and torque delivery.
  • an angular position is reached, in which the recess of the wing in question increasingly opens the radial flow passage through the associated sliding block to the outlet channel, so that rapid pressure relief with exhaust gas discharge takes place.
  • Another important development of the invention provides for cylindrical inner ends on the vanes, which are slidably fitted into cylindrical circumferential recesses of the rotor.
  • a pivotable mounting of the vanes on the outer circumference of the rotor is realized in a very simple manner, where connections to a lubrication channel system can be present. Due to the parallel offset of the axes of rotation of the rotor and segment ring, the blades change their angular position continuously during each revolution.
  • the outer ends of the wings that run past the inside wall of the housing in a contact-free manner can be undercut in the circumferential direction, and preferably the exhaust cutouts are also made in the trailing surface of the wing, for example in the form of cutouts, hollows or the like, optionally with additional exhaust gas guide surfaces.
  • the rotor preferably has inner recesses which are connected to a coolant circulation system, in particular to a lubricating oil circuit, for which purpose the inner rotor recesses are expediently designed as axially parallel, oil-flowed bores, in particular with a flow connection to the cylindrical peripheral recesses.
  • the housing 10 of the combustion chamber turbine has a lower cover 12 and an upper cover 14.
  • the middle part located therebetween has an inner bearing cover 38 in which a segment ring 26 with disks 28 and flange extensions 30 is mounted, which can be integral with one another.
  • a bearing 40 is provided on both sides of a bearing seat 42 (FIG. 2).
  • the axis of rotation of the cement ring 26 is designated A.
  • the axis 1 is offset from this, about which a shaft 20, which is mounted in a roller bearing 46, rotates with an inner rotor 22, which is enclosed by the segment ring 26.
  • the flange extension 30 adjacent to the upper cover 14 carries a non-rotatably mounted gear 44.
  • a further gear 48 is seated on the shaft 20 within the lower cover 12 and is aligned with the gear 44 of the same size at a circumferential point.
  • the two gearwheels 44, 48 mesh with a double gearwheel 54, which is mounted on an output shaft 66 by means of roller bearings 50, 52 near the circumference of the housing (FIG. 3.8).
  • the rotor 22 supports cylindrical inner ends 76 of radially or outwardly projecting vanes 70 in circumferential recesses 78, which in each case pass through sealingly mounted sliding blocks 68 in the ring 26 in a sealed manner.
  • the housing inner wall 34 is not touched by the free outer ends 72 of the wings 70, but which are sealed in the sliding blocks 68 and on the rotor side, for. B. by means of spring tongues 88 in grooves 86 of the wing 70 or by resilient deposits on the disks 28th
  • the segments of the ring 26 are rigidly attached to the front of the disks 28, each of which has an outwardly directed flange shoulder or a hub 30.
  • the clear distance of the disks 28 from one another corresponds to the axial length of the rotor 22.
  • the clear diameter d of the flange projections 30 of the two disks 28 forming the hubs is smaller than the diameter of the rotor 22. Due to the axial displacement a of the segment ring 26 relative to the rotor 22, both remain End faces each have a crescent-shaped passage 60 which connects the space between the rotor 22 and the segment ring 26 with the free cavity in the flange lugs 30.
  • the vanes 70 are pivotally supported on the rotor 22, to which the ring 26 is offset in the middle. Because of this and thanks to the different diameters, the crescent-shaped passage 60 is stationary in its position.
  • An outlet 18 is provided on the outside of the housing 10 adjacent to it, while an inlet 16 is arranged offset in the circumferential direction by approximately 90 to 100 °.
  • a pipe system or an overflow channel 58 in at least one cover can establish the flow connection between inlet 16 and passage 60; 1, 2 and 8 illustrate various air supplies.
  • the housing 10 can have a peripheral region 36 with an increased inside width, to which a housing constriction 64 connects in the direction of the output shaft 66, as a result of which a return connection between the outlet 18 and the inlet 16 or the latter continuing space is avoided.
  • an inner and an outer multi-chamber system 24 or 32 (apart from the mounting of the rotating parts and the vanes) run smoothly in that the inner rotor 22 and the segment ring 26 surrounding it rotate synchronously around the fixed, mutually Rotate offset axes A and I uniformly.
  • These chamber systems are formed in that the vanes 70 pivotally supported on the rotor 22 push the sliding blocks 68 through. Because this happens with the radial sections of the vanes 70 that change during the revolution, these separate the size-variable chambers 24a ... 24f (inside) or 32a ... 32f (outside).
  • the cylindrical inner ends 76 of the vanes 70 are fitted into recesses 78 of the same shape in the rotor 22.
  • the vanes 70 slide back and forth in sliding blocks 68.
  • Each segment of the ring 26 has a partially cylindrical recess on both end faces, so that a two-part cylindrical sliding block 68, in particular with radially offset spring tongues 88, is rotatably or pivotably held between two opposite recesses.
  • each wing 70 has a recess 74 on the surface lagging in the direction of rotation, which forms a radial flow passage in the passage through the associated sliding block 68, preferably through slots 82 with additional exhaust gas guide surfaces 84.
  • top and bottom remain, if appropriate also maintain the wing thickness in the middle for guidance, also on the surface lagging in the direction of rotation.
  • the operation of the combustion chamber turbine is as follows.
  • the vanes 70 passing through the segment ring 26 enter the adjoining channel at the inlet 16, which is formed by the chambers 32a ... 32c located just below in FIG. 1. Since they change from a trailing to a leading angular position due to the approach of the rotor circumference to the segment ring 26, they produce a fan-like effect during about a third revolution.
  • the mixture or air is sucked in through the inlet 16 and pre-compressed.
  • the sucked-in gas either passes directly through one or two pipelines to the associated passage 60 or through the inlet channel formed by the outer chambers 32a ... 32c to the overflow opening 56 of the channel 58, which opens at the passage 60 near the enlarged peripheral zone 36.
  • the actual cargo space i. H. at least one of the inner chambers 24a, etc. (in the position of FIG. 1 just mainly the chambers 24e and 24f), filled as it passed.
  • the main compression which has progressed further in the chamber 24a, begins in the almost completely closed chamber 24f.
  • the ignition triggered by a conventional distributor, preferably by means of glow or spark plugs 90 located in the middle of each segment, the heads 92 of which circulate around the segment ring 26 on one inside Slide the contact cover 94 attached to the bearing cover 38 (Fig. 7).
  • Injection is also possible, in particular in the crescent-shaped passage 60 or in one of the following inner chambers 24f, 24a, 24b, for which the walls may each have a (not shown) check valve which, when passing a stationary injection nozzle - the z. B. may be arranged at the location of the spark plug 90 of segment 26b - is actuated.
  • the inner chambers 24 are dimensioned such that the mixture self-ignites in the smallest chamber 24b.
  • the mixture expanded during combustion is expelled radially or outwards through a wing recess 74, which is only released towards the enlarged outlet 18 in a movement phase or in a certain angular range of the housing 10.
  • the process is repeated with each approaching inner chamber 24 so that charge, compression and combustion take place therein with each revolution.
  • six separate inner chambers 24a ... 24f and six outer chambers 32a ... 32f are formed by six wings 70 which, one after the other - six times in each cycle - cause all the "cycles", that is, suction, pre-compression, compression, Ignition, burning, extension.
  • cycles suction, pre-compression, compression, Ignition, burning, extension.
  • a flow connection to the passage 60 is established after the expansion process, so that the new precompressed filling of the chamber begins with vigorous flushing (at the peripheral point of the chamber 24e). Thanks to the rapid increase in the effective wing area in the direction of rotation, namely during only one third of a revolution, a high pressure and therefore a correspondingly high torque is generated in the increasing volume of the inner chamber (24c, d) after the ignition. 48 is removed. These must have the same diameter so that rotor 22 and segment ring 26 rotate synchronously; because the wings 70 that are movable in phase thereby have a maximum swivel angle predetermined by the axis offset a.
  • the double gear 54 serves not only to ensure the synchronous running of the two ring arrangements 24, 32, but also to deliver the generated torque to the output shaft 66.
  • the mixture supplied provides for the lubrication of the vanes 70 in the sliding blocks 68.
  • the rotor 22 can be hollow, for example with through-openings which are suitable for forced liquid cooling. If this is done using pressure oil, for example, a part of it can be led outside for lubrication purposes.
  • a lubrication system which ensures the continuous supply of the joints 76/78 with lubricant, in particular from the inside of the rotor 22, for example by means of a channel system connected to the pressure oil cooling, is favorable.
  • FIG. 1 An embodiment in which the rotor 22 ends axially in a stepped manner is structurally advantageous, so that a star ring can be inserted as a sealing plate in an axial recess in the end face of the rotor 22, as can be seen from FIG. 1.
  • the sealing cover 96 can be connected to the shaft 20 and the flange extension 30 by means of oil seals or the like, so that its opening is protected from transmission oil and the feed device 55 (21, 29) conveys clean gas to the passage 60.
  • gears 44, 48, 54 or at least one of them are provided with bores 80 or similar openings or are designed as spoke wheels in order to achieve a lighter design without impairing strength. It should be noted that for the sake of simplicity, straight-toothed wheels 44, 48, 54 of the transmission have been drawn; in practice, helical gearing is preferred.
  • the shaft 20 is also possible and provided according to the invention to design the shaft 20 to be hollow at least near the lower cover 12 and to provide it with a check valve 21 and at least one lateral opening 29 in order to provide an air supply directly, sealed against the gear 44/48/54 to effect the passage 60.
  • a pipe connection 98 (as indicated by dots in FIG. 3) from a precompression chamber, e.g. B. the outer chamber 32c, lead to a sealing cover 96 on the flange shoulder 30 (see FIG. 8) in order to bring precompressed gas or mixture directly to the passage 60.
  • a particular advantage of the combustion chamber turbine according to the invention is that, thanks to the great uniformity of the circulation of the multi-chamber system, in which a number of complete working cycles occur in each revolution, a high and even torque output is possible. This makes the variety of suitable applications extraordinarily large.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Ignition Installations For Internal Combustion Engines (AREA)
  • Supercharger (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)
  • Valve Device For Special Equipments (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)
  • Turbine Rotor Nozzle Sealing (AREA)

Claims (20)

1. Moteur à piston rotatif comportant un logement fixe et essentiellement cylindrique (10) ayant des ouvertures d'admission et d'échappement (16,18) et dans les couvercles frontaux (12, 14) duquel est monté un arbre (20) avec un rotor (22) définissant un certain nombre de chambres à volume variable entre des ailettes (70) qui sont disposées de façon à pouvoir se déplacer en phase et en synchronisme vis-à-vis du rotor (22) et qui passent hermétiquement à travers des coulisseaux (68) d'un anneau segmentaire (26) entourant le rotor (22), cet anneau séparant l'un de l'autre un système annulaire de chambre extérieures (32) faisant office de système de précompression et un système annulaire de chambres intérieures (24) faisant office de système de compression principale, ces systèmes annulaires de chambres (32, 24) étant maintenus par une liaison commune à entraînement (figure 3) pour effectuer une rotation centrée sur des axes chacun fixes mais décalés parallèlement l'un de l'autre (A et I), ces systèmes annulaires étant, par ailleurs, reliés l'un à l'autre par écoulement sur des zones périphériques prédéterminées, un dispositif (90, 92, 94) étant prévu pour allumer le mélange carburant/ air comprimé dans la plus petite chambre de compression principale (24b), caractérisé en ce que les ailettes (70) passant devant la paroi intérieure (34) du logement sans la toucher sont montées de façon à pouvoir pivoter sur la périphérie du rotor (22) tandis que, sur leurs faces frontales, on prévoit chaque fois un passage en forme de croissant (60) dont les dimensions et la disposition fixe sont déterminées par le diamètre du rotor et le diamètre (d) d'une collerette à bride (30) adaptée à deux disques (28) fermant axialement l'anneau segmentaire (26).
2. Moteur à piston rotatif suivant la revendication 1, caractérisé en ce que la liaison commune à entraînement (figures 3, 8) comporte une double roue dentée (54) venant s'engrener aussi bien dans une roue dentée (48) maintenue sur l'arbre (20) que dans une autre roue dentée (44) écartée axialement de cette roue dentée (48) et reliée solidairement en rotation à un disque (28) maintenant l'anneau segmentaire (26), de préférence, sur une collerette à bride (30).
3. Moteur à piston rotatif suivant la revendication 2, caractérisé en ce que la double roue dentée (54) est montée à proximité de la périphérie du logement, par exemple, sur l'arbre de sortie (66) au moyen de roulements (50, 52) installés dans le chapeau de palier (38), d'une part, et dans le couvercle supérieur (14), d'autre part, tandis que les deux roues dentées (44, 48) engrenées dans la double roue dentée (54) ont le même pas et le même nombre de dents.
4. Moteur à piston rotatif suivant une des revendications 1 à 3, caractérisé en ce que, en particulier du côté du couvercle, on prévoit un dispositif d'alimentation d'air (55) comportant un canal de transfert (58) qui part d'une zone périphérique du système annulaire de chambres extérieures (32), qui est à peu près diamétralement opposée à l'ouverture d'admission (16) et qui déboche dans une zone périphérique (62) de la collerette à bride (30) dont la position angulaire est proche de celle de l'ouverture d'admission (16).
5. Moteur à piston rotatif suivant la revendication 4, caractérisé en ce que le passage en forme de croissant (60) est en liaison constante par écoulement avec un système de tubes ou avec la zone périphérique (62) de l'embouchure du canal de transfert (58).
6. Moteur à piston rotatif suivant une des revendications 1 à 5, caractérisé en ce que, dans ou à travers le passage en forme de croissant (60), passe un dispositif d'injection de carburant, en particulier, à chaque segment (26a ... 26f) comportant une soupape de retenue s'ouvrant pendant une courte période lors du passage devant un injecteur fixe.
7. Moteur à piston rotatif suivant au moins une des revendications 1 à 6, caractérisé en ce que chaque segment (26a ... 26f) de l'anneau (26) comporte au moins une bougie à incandescence ou une bougie d'allumage (90) dont la tête (92) vient heurter ou entre en contact avec un contacteur (94) adapté dans le couvercle correspondant (12) du logement (10) lors de la rotation de l'anneau segmentaire (26).
8. Moteur à piston rotatif suivant au moins une des revendications 2 à 7, caractérisé en ce que l'anneau segmentaire (26) est étanchéifié vis-à-vis du rotor (22), par exemple, au moyen d'une plaque formant couvercle et faisant ressort, au moyen de languettes flexibles (88) installées dans des rainures périphériques (86) pratiquées du côté du couvercle, ou par des moyens analogues, en particulier, avec des aplatissements en direction des extrémités extérieures libres (72) des ailettes (70).
9. Moteur à piston rotatif suivant au moins une des revendications 1 à 8, des languettes flexibles éant installées dans des rainures pratiquées dans les ailettes du côté du couvercle, caractérisé en ce que, à leurs extrémités extérieures libres (72), les ailettes (70) comportent un évidement (74) qui, lors du passage à travers le coulisseau correspondant (68), forme un passage d'écoulement radial éventuellement avec des surfaces supplémentaires de guidage (84) pour les gaz d'échappement.
10. Moteur à piston rotatif suivant au moins une des revendications 1 à 9, caractérisé en ce que chaque coulisseau (68) comporte deux languettes flexibles ou plus (88) qui viennent s'appliquer tout contre des surfaces planes de l'ailette correspondante (70), en particulier, à des distances radiales différentes de l'extrémité intérieure (76) de cette ailette.
11. Moteur à piston rotatif suivant au moins une des revendications 1 à 10, caractérisé en ce que les extrémités extérieures libres (72) des ailettes (70) comportent des dépouilles dans le sens de rotation.
12. Moteur à piston rotatif suivant au moins une des revendications 1 à 11, caractérisé en ce qu'au moins un des disques (28) situés axialement en aval de l'anneau segmentaire (26) est monté ou réalisé de façon à faire ressort.
13. Moteur à piston rotatif suivant au moins une des revendications 1 à 12, caractérisé en ce que les ailettes (70) comportent des extrémités intérieures cylindriques (76) venant s'adapter, avec possibilité d'y coulisser, dans évidements périphériques cylindriques (78) du rotor (22).
14. Moteur à piston rotatif suivant la revendication 12, caractérisé en ce que les évidements périphériques cylindriques (78) sont raccordés à un système de canaux de lubrification prévu dans le rotor (22).
15. Moteur à piston rotatif suivant au moins une des revendications 1 à 14, caractérisé en ce que le rotor (22) comporte des évidements intérieurs qui sont raccordés à un système de circulation d'un agent réfrigérant.
16. Moteur à piston rotatif suivant la revendication 14 ou 15, caractérisé en ce que les évidements intérieurs du rotor sont réalisés sous forme de passages parallèles à l'axe et dans lesquels circule une huile, ces passages étant, en particulier, en liaison par écoulement avec les évidements périphériques cylindriques (78).
17. Moteur à piston roatif suivant au moins une des revendications à piston rotatif suivant au moins une des revendications à 16, caractérisé en ce que, au moins sur la face frontale située du côté de la prise de force (figure 2), le logement (10) comporte un chapeau de palier intérieur (38) su lequel est monté l'anneau segmentaire (26), ainsi qu'une plaque extérieure (12) sur laquelle est monté l'arbre (20) du rotor (22).
18. Moteur à piston rotatif suivant au moins une des revendications 1 à 17, caractérisé en ce que, à l'échappement (18), le logement (10) comporte une zoné périphérique (36) d'un plus grand diamètre intérieur qui est suivie, en direction de l'alimentation d'air (56), d'un rétrécissement (64) du logement.
19. Moteur à piston rotatif suivant au moins une des revendications 1 à 18, caractérisé en ce qu'on prévoit six ailettes (70) pour former six chambres intérieures (24a ... 24f) et six chambres extérieures (32a ... 32f) qui sont séparées radialement par l'anneau segmentaire (26) comportant six segments (26a ... 26f).
20. Moteur à piston rotatif suivant au moins une des revendications 1 à 19, caractérisé en ce que, à travers la boîte d'engrenages (14, 38) passe un dispositif d'alimentation d'air (55) étanchéifié vis-à-vis des engrenages (44, 48, 54) et réalisé, par exemple, sous forme d'un arbre creux (20) comportant une ouverture latérale (29) en plus de la collerette à bride (30).
EP79104449A 1978-11-28 1979-11-12 Moteur à pistons rotatifs Expired EP0011762B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT79104449T ATE4065T1 (de) 1978-11-28 1979-11-12 Rotationskolbenmotor.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19782851346 DE2851346A1 (de) 1978-11-28 1978-11-28 Brennkammerturbine
DE2851346 1978-11-28

Publications (2)

Publication Number Publication Date
EP0011762A1 EP0011762A1 (fr) 1980-06-11
EP0011762B1 true EP0011762B1 (fr) 1983-07-06

Family

ID=6055701

Family Applications (1)

Application Number Title Priority Date Filing Date
EP79104449A Expired EP0011762B1 (fr) 1978-11-28 1979-11-12 Moteur à pistons rotatifs

Country Status (5)

Country Link
US (1) US4354462A (fr)
EP (1) EP0011762B1 (fr)
JP (1) JPS5914612B2 (fr)
AT (1) ATE4065T1 (fr)
DE (1) DE2851346A1 (fr)

Families Citing this family (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2535393A1 (fr) * 1982-11-02 1984-05-04 Gil Noel Perfectionnements apportes a un moteur rotatif
DE4117936C2 (de) * 1991-05-31 1998-04-02 Andro Caric Rotationskolbenmaschine
DE9207087U1 (de) * 1992-05-26 1992-11-26 Kuechler, Jürgen, Dr., 3556 Weimar Rotationskolbenmaschine
EP0601218B1 (fr) * 1992-11-27 1997-01-22 Andro Caric Machine à piston rotatif
US5616020A (en) * 1993-08-09 1997-04-01 Quik Pump, Inc. Rotary vane pump
US6250279B1 (en) * 1998-01-05 2001-06-26 Steven Zack Rotary internal combustion engine
ITRM20040623A1 (it) * 2004-12-20 2005-03-20 Marzia Murri Camera mobile.
KR101061450B1 (ko) * 2005-11-29 2011-09-02 대니얼 스테크마이어 베인-셀 장치 및 베인-셀 장치를 이용한 폐열 활용 방법
BRPI0704879B1 (pt) * 2007-10-17 2012-10-16 motor de combustão interna, do tipo motor rotativo, provido de diferenciada concepção, durabilidade e desempenho, aplicado em toda sorte de veìculos automotores ou equipamentos industriais.
US20100319654A1 (en) * 2009-06-17 2010-12-23 Hans-Peter Messmer Rotary vane engines and methods
WO2011040895A1 (fr) * 2009-10-02 2011-04-07 Stepanov Sergii Petrovich Mécanisme de transmission
US11434904B2 (en) * 2017-04-28 2022-09-06 Quest Engines, LLC Variable volume chamber device
US10724428B2 (en) * 2017-04-28 2020-07-28 Quest Engines, LLC Variable volume chamber device

Family Cites Families (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US917165A (en) * 1906-10-12 1909-04-06 Carlo Sella Rotary explosive-engine.
DE320708C (de) * 1913-12-18 1920-04-30 Jean Ducruy Explosionskraftmaschine mit kreisendem Kolbenfluegel
US1618806A (en) * 1919-08-02 1927-02-22 Multi Vane Construction Compan Internal-combustion engine
GB194695A (en) * 1922-03-08 1924-04-24 Georges Lecaille Improvements in or relating to internal combustion rotary engines or turbines
FR612489A (fr) * 1926-03-09 1926-10-25 Turbine à combustion interne ou à explosion
US1769822A (en) * 1927-11-16 1930-07-01 Patent Finance And Holding Com Rotary motor
FR813450A (fr) * 1936-11-13 1937-06-01 Mécanismes de moteurs thermiques et de compresseurs
FR912919A (fr) * 1945-03-10 1946-08-23 Dispositif mécanique ayant fonction de pompe, compteur, turbine, etc.
US2789513A (en) * 1955-12-22 1957-04-23 Chester W Johnson Fluid pump
US2864346A (en) * 1957-05-07 1958-12-16 Jr George H Taylor Rotary internal combustion engine
FR1377896A (fr) * 1963-12-23 1964-11-06 Pompe rotative à ailettes ou moteur hydraulique rotatif
SE323839B (fr) * 1964-10-23 1970-05-11 B Agren
US3572985A (en) * 1968-03-19 1971-03-30 Franz Joachim Runge Rotary piston machine
US3813191A (en) * 1972-05-01 1974-05-28 B Foster Rotary vane device for compressor, motor or engine
US3747573A (en) * 1972-05-01 1973-07-24 B Foster Rotary vane device for compressor, motor or engine

Also Published As

Publication number Publication date
JPS5914612B2 (ja) 1984-04-05
EP0011762A1 (fr) 1980-06-11
JPS5581202A (en) 1980-06-19
ATE4065T1 (de) 1983-07-15
US4354462A (en) 1982-10-19
DE2851346A1 (de) 1980-05-29

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