US20120237370A1 - Engine having rotary pistons - Google Patents

Engine having rotary pistons Download PDF

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Publication number
US20120237370A1
US20120237370A1 US13/500,219 US201013500219A US2012237370A1 US 20120237370 A1 US20120237370 A1 US 20120237370A1 US 201013500219 A US201013500219 A US 201013500219A US 2012237370 A1 US2012237370 A1 US 2012237370A1
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US
United States
Prior art keywords
mechanism according
guide means
enclosure
rotary assembly
piston
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.)
Abandoned
Application number
US13/500,219
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English (en)
Inventor
Philippe Kuzdzal
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.)
PK ENR
Original Assignee
PK ENR
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Filing date
Publication date
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Assigned to PK-ENR reassignment PK-ENR ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: KUZDZAL, PHILIPPE
Publication of US20120237370A1 publication Critical patent/US20120237370A1/en
Abandoned 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
    • F01C1/40—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 having a hinged member
    • F01C1/44—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 having a hinged member with vanes hinged to the inner 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
    • 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
    • F01C1/067—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 cam-and-follower 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
    • F01C1/07—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 crankshaft-and-connecting-rod 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
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/08—Rotary pistons
    • 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
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/10—Outer members for co-operation with rotary pistons; Casings
    • F01C21/104—Stators; Members defining the outer boundaries of the working chamber
    • F01C21/106—Stators; Members defining the outer boundaries of the working chamber with a radial surface, e.g. cam rings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2270/00—Control; Monitoring or safety arrangements
    • F04C2270/12—Vibration

Definitions

  • the present invention relates to a rotary piston mechanism as well as an engine and pump using such a mechanism.
  • Rotary piston mechanisms and in particular in their motor application, have been described in many documents, which define the geometric principles of the movement of a polygon articulated at the apices of the sides making it up; each of the sides all having the same length and each of the apices being in geometric contact with a stator shape.
  • This mechanical approach appears correct and therefore consists of determining the movement of the articulations of the polygons without action by the stator on the apex of the polygon.
  • Patent WO 01/88341 A1 proposes a solution describing the chaining of four pistons to one another using connecting rods also performing the appropriate transfer function between the pistons and the transmission shaft, as well as several mechanical solutions resolving the transfer function between the tangential speed variations of the pistons toward the central transmission shaft rotating at a constant speed, in particular using rollers traveling over a rolling surface installed on the lateral flanges.
  • connection between pistons does not appear capable of sustainably bearing the intense pulling, thrust, and centrifugal forces to which it will be subjected.
  • These bowed collaborating movable interlocking forms are complex in terms of expansions, buttress formation, friction distribution, and their use is as difficult as it is unreliable.
  • the sealing of such pieces is also more complex to achieve than the sealing of traditional axles and not very effective inasmuch as the stressed orientation of the sealing segment does not correspond to the forces undergone by that piece.
  • a machining anomaly, on the rolling surfaces, will result in a positioning error of the apex of the diamond, the sealing piece of which will be the only one to react this additional force.
  • This piece will be stressed in its degree of freedom and may no longer pivot and will break; this stress may potentially be passed on to the connection between the pistons.
  • Patent EP 1 295 012 B1 and part of patent US 2004/0089251 A1 also propose determining the deformation of the polygon without bearing on the stator enclosure. This proposed solution uses a set of gears.
  • patent US 2004/0089251 A1 proposes a geometric solution accumulating the sealing function and a geometric function.
  • the invention therefore aims to propose a technical solution making it possible to do away with these operating difficulties due to machining imprecisions, expansion phenomena due to the temperature or other factors, and wear phenomena of the pieces.
  • the present invention relates to a rotary piston mechanism comprising an outer enclosure forming a stator inside which a rotary assembly forming a rotor moves, the rotary assembly comprising a plurality of pistons forming an articulated polygon, each piston delimiting a volume chamber with the enclosure, and first guide means arranged to cooperate with second guide means comprising rolling surfaces, so as to stress the polygon to perform a predetermined movement, wherein the mechanism comprises a return device maintaining contact between the guide means and the rolling surfaces.
  • the first and second guide means allow the pistons to follow a predetermined direction so as to limit the action of the enclosure on the apices of the polygon while the return device makes it possible to offset the machining defects of the guide means as well as the expansion and wear of those elements occurring during operation of the mechanism.
  • the return device is supported by the rotary assembly.
  • the return device comprises a plurality of dampers positioned between a stationary point of each piston and a movable fastening point of each of the first guide means, such as the guide roller axis of rotation.
  • This arrangement makes it possible to offset the wear of each of the guide rollers individually.
  • rollers make it possible to distribute the forces applied on the guide surfaces. Furthermore, these rollers have a small bulk and limit the friction on the guide surfaces due to their degree of rotational freedom.
  • the guide rollers are conical.
  • the second guide means are rolling surfaces with an equal slope.
  • the return device is supported by the outer enclosure.
  • This arrangement makes it possible to place the return device at stationary points and limit the number thereof.
  • the second guide means are supported by lateral flanges positioned coaxially to the outer enclosure and serving to close the latter part.
  • This arrangement makes it possible to take advantage of the ease of assembling and disassembling the flanges used to close the outer enclosure so as to position the second guide means therein. It is also possible to consider manually pre-adjusting the orientation of said second adjustment means using a suitable device before closing of the enclosure by the flanges.
  • the second guide means comprise two sectors, the first of which is secured to the stator enclosure and the second of which is translationally movable relative to the first, a return device being positioned between a stationary point of the first sector and a movable point of the second sector of each of the second guide means.
  • This arrangement makes it possible to be able to modify the eccentricity of the guide surfaces, which assume a substantially ellipsoidal form, and thus makes it possible to offset the general wear of the guide surfaces as well as their machining defects.
  • a segment support device is pivotably mounted along a single axis on each of the apices of the polygon.
  • This arrangement allows the segment support device to adapt to the shape of the enclosure and to present the segments at all times in a direction transverse to the wall of the stator in which they evolve, which reduces the wear of the segments and imparts better sealing to the volume chambers.
  • a segment support device comprises a device for pressing segments on the stator enclosure.
  • This arrangement is to produce a continuous sliding contact of the segments on the inner surface of the single-piece body so as to offset the machining defects thereof and therefore further improve the sealing between the volume chambers.
  • At least one piston is connected by a single connecting rod ( 24 ) or by several connecting rods ( 241 , 242 ) having the same hinge pins as the transmission shaft ( 40 ).
  • connecting rods is geometrically easier to design than a set of gears, for example, and will be a source of less play due to the reduced number of elements and connections.
  • the invention consists of keeping only one connecting rod per piston, for example that defined as rear in patent WO 01/88341 A1 in the case of rotation in the indirect trigonometric direction or in the clockwise direction.
  • two adjacent pistons are connected to one another by a pivot link with an axis parallel to the axis of rotation of the rotary assembly.
  • This configuration makes it possible to obtain a connection of two adjacent pistons that is both very solid and flexible, and is also easy to produce, as it only comprises a single pin fitted into both ends of the two pistons.
  • the rolling surfaces are turned toward the axis of rotation of the rotary body.
  • the rotary assembly comprises a lubrication circuit mounted in a closed circuit.
  • This arrangement makes it possible to use a so-called “dry sump” lubrication system with all of the advantages thereof, in particular more significant and targeted lubrication at the critical locations, a lowered center of gravity of the mechanism due to the lack of an oil pan under the mechanism, a reservoir outside the mechanism that is not very bulky, and the possibility of incorporating a heat exchanger for cooling oil in the lubrication circuit.
  • the distance between the connecting pin between two adjacent pistons and the hinge pin of the segment support device is constant.
  • the distance between the connecting pin between pistons and the hinge pin of the segment support device is variable.
  • This arrangement makes it possible to obtain maximal volume ratios between chambers to the extent that the segment support devices and segments still perform their sealing function.
  • the segment support device comprises a complementary device for pressing segments on the stator, such as a hydraulic piston.
  • This arrangement offers the possibility of being able to still further increase the volume ratios between chambers by offering the segment supports and segments the possibility of ensuring sealing of the volume chambers despite substantial spacing of the wall of the stator for certain positions of the pistons.
  • the present invention also relates to a pump comprising a mechanism as described above as well as an engine using the same mechanism in its use for producing mechanical energy.
  • FIG. 1 shows a summary projection diagram of the profile of the mechanism according to the invention.
  • FIG. 2 shows a summary projection diagram of the profile of the mechanism with a first embodiment of the arrangement of the play compensating device.
  • FIG. 3 shows a summary projection diagram of the profile of the mechanism with a second embodiment of the arrangement of the play compensating device.
  • FIG. 4 shows the arrangement of three pistons in perspective view positioned outside the stator enclosure.
  • FIG. 5 is a perspective view of a second guide means with its play compensating device according to the embodiment illustrated in FIG. 3 .
  • FIG. 6 is a perspective view of the inner portion of a flange incorporating the second guide means with its play compensating device illustrated in FIG. 5 .
  • FIG. 7 is a perspective view of the outer portion of the flange illustrated in FIG. 6 .
  • FIG. 8 shows a cross-sectional and profile view of the mechanism according to the invention.
  • FIG. 9 shows a cross-sectional view of a hydraulic damper of the mechanism according to the invention.
  • a rotary piston 21 mechanism 1 includes an outer enclosure 2 forming a stator inside which a rotary assembly 20 forming a rotor moves.
  • the outer enclosure 2 in the embodiment illustrated in FIGS. 1 , 2 , 3 and 8 includes a single-piece body 3 generally made from steel, forming a volume with two identical ellipsoidal bases, in which an ellipsoid-shaped through cavity 5 is bored.
  • the inner surface 4 of said cavity 5 is advantageously glazed so as to give it a surface state satisfactory for the applications of the mechanism 1 .
  • the outer enclosure 2 also includes two lateral ellipsoid-shaped flanges 6 a , 6 b, shown in FIGS. 6 and 7 , closing the through cavity 5 at each of the two ellipsoidal bases of the single-piece body 3 .
  • Each of said flanges 6 a, 6 b is screwed to the single-piece body 3 of the enclosure 2 and incorporates sealing means such as an O-ring positioned in a groove situated on the joint of the flanges 6 a, 6 b with the single-piece body 3 .
  • Each of the flanges 6 a, 6 b comprises a bearing 8 a, 8 b centered to allow the rotation of the transmission shaft 40 along the axis 30 of the bearings 8 a, 8 b.
  • Each of these bearings 8 a, 8 b is respectively secured by screws 18 a to each of the flanges 6 a, 6 b and comprises two cushions on the inner contour 18 b thereof as well as an oil seal flush on the outer surface 18 c of each of the bearings 8 a, 8 b so as to perform oil sealing between the barriers 8 a, 8 b in the transmission shaft 40 .
  • guide means 7 a, 7 b having a volume shape with substantially ellipsoidal bases 19 a generating a first rolling surface 10 a and a second rolling surface 10 b of revolution on the outer contour 19 b of these same substantially ellipsoidal bases 19 a, are positioned coaxially to the alignment axis 30 of the two flanges 6 a, 6 b and oriented towards the inside of the enclosure 2 . They are fastened using screws 9 a passing through each of the bearings 8 a, 8 b from the outside towards the inside of the flanges 6 a, 6 b and being screwed on threaded bores 9 b positioned opposite the screws 9 a on each of the guide means 7 a, 7 b.
  • the substantially ellipsoidal guide means 7 a, 7 b are coaxial and have a slight rotational offset along their axis 30 .
  • Each of said guide means 7 a, 7 b has an ellipsoidal central opening 11 whereof the small axis has a size larger than the diameter of the bearings 8 a, 8 b so as not to bother the rotation of the transmission shaft 40 .
  • these guide means 7 a, 7 b are made in a single piece having a predefined shape not evolving during use of the mechanism 1 .
  • these guide means 7 a, 7 b comprise two sectors 71 and 72 separating the substantially ellipsoidal volume into two volumes at the small axis thereof, thereby creating four coplanar and distinct cutting surfaces 12 a, 12 b, 12 c and 12 d on each of the sectors 71 and 72 , each of the surfaces of a same sector 71 being opposite a surface of the other sectors 72 while being parallel thereto.
  • the sector 71 is fastened to the bearings 8 a, 8 b using screws 9 a tightening in the threaded bores 9 b, the second sector 72 is slidingly mounted in translation relative to the sector 71 .
  • the two sectors 71 and 72 have a first mechanical link 13 formed by a pin positioned between two first surfaces 12 a, 12 b opposite the sectors 71 and 72 . This pin 13 is secured on the surface 12 a and slides translationally in a bore positioned on the surface 12 b.
  • a second mechanical link 14 is formed in the same way between the other two opposite surfaces 12 c, 12 d. However, the axis 14 of this link is surrounded by conical washers 15 acting in compression, such as a spring, and acting as a play compensating device 50 .
  • positioned on each of the edges of the two sectors 71 and 72 of each of the guide means 7 a and 7 b is a joint 16 of the cantilever comb expansion type.
  • joints 16 are made up of a set of identical parallelepiped teeth 17 a, spaced apart by a same distance and coming transversely from the cutting surfaces 12 a, 12 c of the sector 71 , and by another set of teeth 17 a coming transversely from the cutting surfaces 12 b, 12 d of the sector 72 respectively located opposite the cutting surfaces 12 a, 12 c of the sector 71 , each set of teeth 17 a fitting into the spaces 17 b between teeth 17 a created by the other set of teeth 17 a.
  • the rotary assembly 20 forming a rotor is made up of four pistons 21 forming a deformable diamond.
  • the pistons 21 have a convex shape on the outer surface 21 a thereof and a planar shape on the inner surface 21 b thereof.
  • Each of the adjacent pistons 21 is solidly connected using a pivot link made up of a pin 22 passing transversely through the ends of two adjacent pistons 21 .
  • Each piston 21 has a parallelepiped recess 23 whereof two walls 23 a, 23 b are positioned transversely to the pins 22 ensuring the connection of the adjacent pistons 21 .
  • a connecting rod 24 is positioned here made up of two connecting rods 241 , 242 positioned side-by-side and separated by a space 24 c. These two connecting rods 241 , 242 are maintained by a pivot link formed by a pin 25 passing transversely through the two walls 23 a, 23 b as well as the head 24 a of each of the two cylindrical connecting rods 241 , 242 . This pin 25 is thus positioned parallel to the pins 22 , linking the adjacent pistons 21 to one another.
  • Each of the pistons 21 also comprises two through openings 26 a, 26 b , which are also parallel to the axes 22 , and made on the lower portion of the piston 21 on either side of the recess 23 . These two openings 26 a, 26 b are intended each to receive a first guide means 27 , illustrated in FIGS. 1 , 2 , 3 and 8 by rollers 27 .
  • Each of the pistons 21 only comprises two rollers 27 each positioned on the lateral surfaces 21 c, 21 d of the piston 21 .
  • a front guide roller 27 a and a rear guide roller 27 b are distinguished whereof the axes of rotation are on either side of the recess 23 coaxial to each the openings 26 a, 26 b.
  • the piston 21 has a suitable profile on either side allowing the rotation of each of said two rollers 27 a and 27 b.
  • each piston 21 has a semicircular transverse notch 28 on the width of the piston 21 .
  • a segment support device 29 having, like the notch 28 , a semicircular shape allowing it pivot in the notch 28 along the hinge pin 32 of the segment support device 29 .
  • segment support device 29 On said segment support device 29 , two radial segments 31 are positioned protruding from the convex surface 21 a of the piston 21 . Each of these segments 31 is pushed toward the outside of the device 29 by the action of a spring 33 positioned in the device 29 .
  • the distance between the linking pin 22 of two adjacent pistons 21 and the hinge pin 32 of the segment support device 29 is constant.
  • each of the connecting rods 24 is, as already mentioned above, made up of two connecting rods 241 , 242 positioned side-by-side and separated by a space 24 c.
  • Each of these two connecting rods 241 , 242 is connected to a transmission shaft 40 by means of the pivot link made by a pin 34 passing transversely through the foot 24 b of each of the cylindrical connecting rods 241 , 242 on the one hand, and on the other hand, a hub 41 of the transmission shaft 40 passing in the space 24 c positioned between the feet 24 b of the two connecting rods 241 , 242 .
  • the two guide rollers 27 a and 27 b present on the lateral surfaces 21 c, 21 d of each piston 21 are connected thereto by means of a return device 50 or play compensating device such as hydraulic dampers 50 , illustrated in FIG. 9 .
  • a hydraulic damper 50 is made up of a piston-cylinder assembly whereof the internal leaks are calibrated.
  • the piston 51 is pierced at the center thereof with a calibrated diameter and the ball 53 , provided with a spring 54 acting as a check valve, imposes the passage direction of the oil through the calibrated space 55 between the piston 51 and the cylinder 52 .
  • a stationary connection by means of a screw (not shown) is made between the piston 21 and the first fastener 56 of the hydraulic damper 50 and a pivot link is made by means of a pin (not shown) between the second link 57 of the hydraulic damper 50 and the axis of rotation 27 c of a roller 27 .
  • the rotary assembly 20 is assembled, it is inserted inside the single-piece body 3 and enclosed inside the stator enclosure 2 during mounting of the lateral flanges 6 a, 6 b.
  • the rotary assembly 20 delimits, with the stator enclosure 2 , volume chambers 35 .
  • a closed oil circuit (not shown) is arranged in the various parts of the rotary assembly 20 so as to lubricate the contact areas between the different moving pieces relative to one another, as is the case for the pins 25 and 34 respectively maintaining the head 24 a and the foot 24 b of the connecting rods 24 .
  • This so-called dry sump circuit includes an oil pump as well as an oil reservoir, which are both positioned outside the stator enclosure 2 .
  • a heat exchanger is also arranged in the oil circuit so as to cool it.
  • the mechanism 1 can be used as an engine so as to produce torque on its transmission shaft 40 , or as a pump by driving that same transmission shaft 40 using a coupling connecting it to an external engine.
  • the apices of the diamond formed by the four pistons 21 thus follow the trajectory of the inner surface 4 of the single-piece body 3 of the stator enclosure 2 without bearing on that same surface 4 .
  • the segments 31 by means of the spring 33 present in the segment support device 29 ensure continuous sliding contact on the inner surface 4 of the single-piece body 3 of the stator enclosure 2 .
  • connection of the segment support device 29 in its notch 28 guarantees the segments 31 radial contact with the inner surface 4 of the single-piece body 3 of the stator enclosure 2 , which makes it possible to reduce the wear thereof and preserve good sealing of the volume chambers 35 .
  • the hydraulic dampers 50 arranged on each of the rollers 27 will offset that wear at all times by providing continuous contacts between the rollers 27 and the two rolling surfaces 10 a and 10 b.
  • the rolling surfaces 10 a and 10 b in the embodiment thereof with two sectors 71 and 72 will increase the perimeter of their rolling surface 10 a, 10 b so as to compensate the wear of the rollers 27 .
  • the segment support device 29 can comprise a complementary device for pressing the segments 31 on the inner surface 4 of the single-piece body 3 of the outer stator enclosure 2 so as to make it possible to use a different stator profile and increase the volume ratio between the volume chambers 35 , and the return device 50 illustrated here by the dampers 50 may be of any type, on the condition it provides contact between the guide means ( 27 , 27 a, 27 b ) and the rolling surfaces ( 10 a, 10 b ).

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Hydraulic Motors (AREA)
  • Transmission Devices (AREA)
  • Reciprocating Pumps (AREA)
US13/500,219 2009-10-05 2010-10-04 Engine having rotary pistons Abandoned US20120237370A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
FR0956912A FR2950926B1 (fr) 2009-10-05 2009-10-05 Moteur a pistons rotatifs
FR0956912 2009-10-05
PCT/FR2010/052087 WO2011042648A2 (fr) 2009-10-05 2010-10-04 Moteur à pistons rotatifs

Publications (1)

Publication Number Publication Date
US20120237370A1 true US20120237370A1 (en) 2012-09-20

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ID=42153864

Family Applications (1)

Application Number Title Priority Date Filing Date
US13/500,219 Abandoned US20120237370A1 (en) 2009-10-05 2010-10-04 Engine having rotary pistons

Country Status (4)

Country Link
US (1) US20120237370A1 (fr)
EP (1) EP2486239A2 (fr)
FR (1) FR2950926B1 (fr)
WO (1) WO2011042648A2 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2021232025A1 (fr) * 2020-05-15 2021-11-18 Lumenium Llc Machine rotative à transmission entraînée par moyeu articulant une tringlerie à quatre barres
ES2897124A1 (es) * 2020-08-27 2022-02-28 Abascal Gonzalez Juan Angel Motor térmico rotativo "en cruz"

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR3095238A1 (fr) * 2019-04-18 2020-10-23 Hervé BOURET Moteur rotatif comprenant un rotor annulaire articulé muni d’ailettes pivotantes à effet de levier

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19901110C2 (de) * 1999-01-14 2002-06-06 Herbert Huettlin Schwenkkolbenmaschine
DE10001962B4 (de) * 2000-01-18 2004-07-22 Hüttlin, Herbert, Dr.h.c. Rotationskolbenmaschine
WO2001088341A1 (fr) * 2000-05-12 2001-11-22 Peter Szorenyi Moteur a combustion interne possedant un rotor articule
CA2310488A1 (fr) 2000-05-23 2001-11-23 Normand Beaudoin Polyturbine energetique et antirefoulement
US20040089251A1 (en) 2001-04-02 2004-05-13 Talero John Alejandro Sanchez Water cooled rotary internal combustion machine
WO2004070169A1 (fr) * 2003-02-10 2004-08-19 Gilles Saint-Hilaire Moteur rotatif

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2021232025A1 (fr) * 2020-05-15 2021-11-18 Lumenium Llc Machine rotative à transmission entraînée par moyeu articulant une tringlerie à quatre barres
ES2897124A1 (es) * 2020-08-27 2022-02-28 Abascal Gonzalez Juan Angel Motor térmico rotativo "en cruz"

Also Published As

Publication number Publication date
WO2011042648A3 (fr) 2012-04-05
EP2486239A2 (fr) 2012-08-15
FR2950926A1 (fr) 2011-04-08
FR2950926B1 (fr) 2011-12-02
WO2011042648A2 (fr) 2011-04-14

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