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 and a motor and pump using such a mechanism.
• Rotary piston mechanisms and in particular in their driving application have been described in numerous documents which define the geometric principles of the displacement of an articulated polygon at the vertices of the component sides; each of the sides all having the same length and each of the vertices being in geometric contact with a stator shape.
• Patent WO 01/88341 A1 proposes a solution describing the chaining of four pistons to each other by means of connecting rods also ensuring the appropriate transfer function between the pistons and the transmission shaft, as well as several mechanical solutions solving the transfer function. between the tangential velocity variations of the pistons towards the central transmission shaft rotating at a constant speed, in particular using rollers traversing a running surface installed on the lateral flanges.
• the project as described proposed a hyperstatic configuration that allowed no tolerance of games.
• the trapezoid described by the two rods of the two adjacent pistons, the point of connection of the pistons and the connection point on the motor shaft builds a hyperstatic connection.
• This trapezium is indeformable and can not admit any variation in length of any of its sides as will be the case when using the mechanism that will reveal expansion phenomena.
• the bearings of the joints will be weakened organs. These parts will be worn prematurely having generated internal friction making the mechanism unsuitable for its purpose.
• connection between pistons does not seem to be able to sustainably support the intense stresses of traction, thrust and centrifugal force to which it will be subjected.
• arched collaborating mobile interlocking are complex in terms of dilatation, bow formation, friction distribution and their implementation. work is more difficult than unreliable.
• the sealing of such parts is also more complex to achieve than the conventional axis sealing and inefficient insofar as the constrained orientation of the sealing segment does not match the forces experienced by this part.
• a machining anomaly, on the bearing surfaces, will result in a positioning error of the top of the diamond, of which the sealing piece will be alone to take this additional effort.
• This piece will be constrained in its degree of freedom and can no longer pivot and break; possibly this constraint will be reported on the connection between pistons.
• EP 1 295 012 B1 and in part US Patent 2004/0089251 A1 also propose to determine the deformation of the polygon without relying on the stator chamber. This proposed solution using a set of gears.
• US Patent 2004/0089251 A1 proposes a geometric solution combining a sealing function and a geometric function.
• the subject of the present invention is a rotary piston mechanism comprising an outer stator enclosure inside which a rotary rotor assembly moves, the rotary assembly comprising a plurality of pistons forming an articulated polygon, each piston defining with the enclosure a volumetric chamber, and first guide means arranged to cooperate with second guide means comprising rolling surfaces, in order to constrain the polygon to perform a predetermined movement, the mechanism being characterized in that it comprises a return device maintaining contact between the guide means and the running surfaces.
• the first and second guide means allow the pistons to follow a predetermined direction in order to limit the action of the enclosure on the polygon vertices while the return device makes it possible to compensate for the machining defects of the guide means as well as the dislocation and use of these elements occurring during the operation of the mechanism.
• the return device is carried by the rotary assembly.
• the return device comprises a plurality of dampers arranged between a fixed point of each piston and a movable attachment point of each of the first guide means, such as the axis of rotation of guide rollers.
• This arrangement makes it possible to individually compensate the wear of each of the guide rollers.
• rollers make it possible to distribute the forces applied on the guide surfaces.
• these rollers have a small footprint and limit friction on the guide surfaces by their degree of freedom in rotation.
• the guide rollers are tapered.
• the second guide means are rolling surfaces of equal slope.
• the return device is carried by the outer enclosure.
• This arrangement makes it possible to set up the return device at fixed points and to limit their number.
• the second guide means are carried by lateral flanges arranged coaxially with the outer enclosure and serving to close it.
• This arrangement allows to take advantage of the ease of assembly and disassembly of the flanges used to close the outer enclosure in order to have the second guide means. It may also be envisaged to carry out a manual presetting of the orientation of these second adjustment means by an appropriate device before closure of the enclosure by the flanges.
• the second guide means comprise two sectors, the first of which is fixed to the stator enclosure and the second is movable in translation relative to the first, a return device being disposed between a fixed point of the first sector and a moving point of the second sector of each of the second guide means.
• This arrangement makes it possible to modify the eccentricity of the bearing surface, which has a substantially ellipsoidal shape, and thus makes it possible to compensate for the general wear of the guide surfaces as well as their machining defects.
• a segment-holder device is pivotally mounted along a single axis on each of the vertices of the polygon.
• This arrangement allows the segment holder device to adapt to the shape of the enclosure and to present the segments at each moment in a direction transverse to the wall of the stator in which they evolve, which reduces the wear of the segments and confers a better sealing of the volumetric chambers.
• a segment ispositif comprises a device for pressurizing the segments on the stator enclosure.
• At least one piston is connected by a single link (24) or by several links (241, 242) having the same pivot axes to the transmission shaft (40).
• links are geometrically easier to design than a set of gears for example and will be a lesser source of games because of the number of elements and reduced links.
• the invention consists in keeping only one rod per piston, for example that being defined as posterior in patent WO 01/88341 A1 in the case of a rotation in the indirect trigonometric direction or in a clockwise direction.
• two adjacent pistons are interconnected by a pivot connection axis parallel to the axis of rotation of the rotary assembly.
• This configuration makes it possible to obtain a very solid and flexible connection at the same time from two adjacent pistons, moreover it is simple to carry out since it comprises only one axis fitted into the two ends of the two pistons.
• the rolling surfaces are turned towards the axis of rotation of the rotating body.
• the rotary assembly comprises a lubrication circuit mounted in a closed circuit.
• the distance between the connecting axis between two adjacent pistons and the pivot axis of the segment-carrier device is constant. This arrangement makes it possible to define a particular stator profile corresponding to this geometrical constraint that will only give the segment-holders and segments their sealing function between volumetric chambers.
• the distance between the connecting axis between the piston and the pivot axis of the segment-carrier device is variable.
• This arrangement makes it possible to obtain maximum volumetric ratios between chambers in the limit where the segment-holder and segment devices still perform their sealing function.
• the segment carrier is provided with a complementary device for pressurizing the segments on the stator, such as a hydraulic piston.
• This arrangement offers the possibility of being able to increase even more volumetric ratios between chambers by offering the possibility to segment holders and segments to seal the volumetric chambers despite a substantial spacing of the stator wall for certain positions of the pistons.
• the present invention also relates to a pump comprising a mechanism as described above and a motor using the same mechanism in its use of mechanical energy production.
• Figure 1 shows a schematic block diagram of the profile of the mechanism according to the invention.
• FIG. 2 shows a block diagram of the profile of the mechanism with a first embodiment of the arrangement of the gaming retrofit device.
• Figure 3 shows a schematic block diagram of the profile of the mechanism with a second embodiment of the arrangement of the game retrieval device.
• FIG. 5 is a perspective view of a second guide means with its game-catching device according to the embodiment illustrated in FIG. 3.
• FIG. 6 is a perspective view of the interior portion of a flange integrating the second guide means with its game-catching device illustrated in FIG. 5.
• Figure 7 is a perspective view of the outer portion of the flange shown in Figure 6.
• Figure 8 shows a sectional and side view of the mechanism according to the invention.
• Figure 9 shows a sectional view of a hydraulic damper mechanism according to the invention.
• a rotary piston mechanism 1 comprises an outer stator enclosure 2 inside which a rotary rotor assembly 20 operates.
• the outer enclosure 2 in the exemplary embodiment illustrated in FIGS. 1, 2, 3 and 8 comprises a one-piece body 3 generally made of steel, forming a volume with two identical elliptical bases, in which a through cavity 5 is bored. elliptical shape.
• the inner surface 4 of this cavity 5 is advantageously glazed so as to impart a satisfactory surface condition to the applications of the mechanism 1.
• the outer enclosure 2 also comprises two lateral flanges 6a, 6b ellipse-shaped, shown in Figures 6 and 7, closing the through cavity 5 at each of the two ellipsoidal bases of the one-piece body 3.
• Each of these flanges 6a, 6b is referred to the one-piece body 3 of the chamber 2 and includes sealing means such as an O-ring disposed in a groove located on the joint of the flanges 6a, 6b with the one-piece body 3.
• Each of the flanges 6a, 6b comprises a bearing 8a, 8b centered to allow the rotation of a transmission shaft 40 along the axis 30 of the bearings 8a, 8b.
• Each of these bearings 8a, 8b is respectively fixed by screws 18a to each of the flanges 6a, 6b and comprises two pads on its inner contour 18b and a seal SP I flush with the outer face 18c of each of the bearings 8a, 8b in order to achieve oil sealing between the bearings 8a, 8b and the transmission shaft 40.
• guide means 7a, 7b having a volumetric shape of substantially ellipsoidal bases 19a generating a first rolling surface 10a and a second rolling surface 10b of revolution on the outer contour 19b of these same substantially ellipsoidal bases 19a, are de posed coaxially with the alignment axis 30 of the two flanges 6a, 6b and directed towards the inside of the enclosure 2. Their fixing is ensured by means of screws 9a passing through each of the palms. 8a, 8b from the outside to the inside of the flanges 6a, 6b and being screwed onto threaded bores 9b facing the screws 9a on each of the guide means 7a, 7b.
• the two guiding means 7a, 7b of substantially ellipsoidal shape are coaxial and have a slight offset in rotation along their axis 30.
• Each of these guiding means 7a, 7b has a central opening 1 1 of ellipsoidal shape whose short axis presents a dimension greater than the diameter of the bearings 8a, 8b so as not to hinder the rotation of the transmission shaft 40.
• these guide means 7a, 7b are made in one piece having a predefined shape that does not evolve during the use of the mechanism 1.
• these guide means 7a, 7b comprise two sectors 71 and 72 separating the volume of substantially ellipsoidal shape into two volumes at its minor axis, thus generating four coplanar and distinct cutting surfaces 12a, 12b, 12c and 12d on each of the sectors 71 and 72, each of the surfaces of the same sector 71 facing a surface of the other sector 72 while being parallel to it.
• the sector 71 is fixed to the bearings 8a, 8b by means of the screws 9a tightening in the threaded bores 9b, the second sector 72 is slidably mounted in translation relative to the sector 71.
• the two sectors 71 and 72 have a first mechanical connection 13 formed by an axis disposed between two first surfaces 12a, 1 2b facing sectors 71 and 72. This axis 13 is fixed on the surface 12a and slides in translation in a bore disposed on the surface 12b.
• a second mechanical connection 14 is formed in the same way between the two other surfaces 1 2c, 1 2d opposite. However, the axis 14 of this connection is surrounded by conical washers 15 acting in compression such as a spring and acting as a game-catching device 50.
• seal 16 of the comb type console In order to ensure the continuity of the running surfaces 10a and 10b deformable to adapt to the relative translational movements of the two adjacent edges of the two sectors 71 and 72, it is disposed on each of the edges of the two sectors 71 and 72 of each of the guide means 7a and 7b, a seal 16 of the comb type console.
• These seals 16 are constituted by a set of parallelepiped-shaped identical teeth 17a, spaced at the same distance and issuing transversely from the cutting surfaces 12a, 12c of the sector 71, and by another set of teeth 17a issuing transversely from the cutting surfaces. 1 2b, 12d of the sector 72 respectively facing the cutting surfaces 12a, 12c of the sector 71, each set of teeth 17a interlocking in the spaces 17b between teeth 17a generated by the other set of teeth 17a.
• the rotary assembly 20 forming a rotor is formed by four pistons 21 forming a deformable rhombus.
• the pistons 21 have a convex shape on their outer face 21a and a flat shape on their inner face 21b.
• Each of the adjacent pistons 21 are firmly connected by means of a pivotal connection consisting of an axis 22 traversing transversely the ends of two adjacent pistons 21.
• Each piston 21 has a recess 23 of parallelepipedal shape, two walls 23a, 23b of which are arranged transversely to the pins 22 connecting the adjacent pistons 21.
• a rod 24 composed here of two links 241, 242 arranged side by side and separated by a spacing 24c. These two links 241, 242 are held by a pivotal connection real marina by an axis 25 traversing transversely the two walls 23a, 23b and the head 24a of each of the two rods 241, 242 of cylindrical shape.
• This axis 25 is thus arranged parallel to the pins 22 connecting the pistons 21 adjacent to each other.
• Each of the pistons 21 also comprises two orifices 26a, 26b crossing, also parallel to the pins 22, and made on the lower part of the piston 21 on either side of the recess 23. These two orifices 26a, 26b are intended for each receive a first guiding means 27 illustrated in Figures 1, 2, 3 and 8 by rollers 27.
• Each of the pistons 21 comprises only two rollers 27 each disposed on the lateral faces 21c, 21d of the piston 21. According to the direction of rotation of the rotary assembly 20, an anterior guide roller 27a and a posterior guide roller 27b whose axes of rotation are located on either side of the recess 23 are coaxially orifices 26a, 26b.
• the piston 21 has on both sides a suitable profile allowing the rotation of each of these two rollers 27a and 27b.
• each piston 21 has a semi-circular notch 28 across the width of the piston 21.
• a segment-carrying device 29 having, like the notch 28, a semicircular shape that allows it to pivot in the notch 28 along the axis 32 of pivoting of the door device. -segments 29.
• segment-carrier device 29 there are two radial segments 31 coming protruding from the convex surface 21a of the piston 21. Each of these segments 31 is pushed towards the outside of the device 29 by the action of a spring 33 placed in the device 29.
• the distance between the connection axis 22 of two adjacent pistons 21 and the pivot axis 32 of the segment-carrier device 29 is constant.
• each of the rods 24 is, as already mentioned above, composed of two rods 241, 242 arranged side by side and separated by a spacing 24c.
• Each of these two links 241, 242 is connected to a transmission shaft 40 by means of a pivot connection made by an axis 34 traversing transversely on the one hand the foot 24b of each of the cylindrical rods 241, 242. and on the other hand a hub 41 of the transmission shaft 40 passing in the spacing 24c disposed between the feet 24b of the two rods 241, 242.
• a hydraulic damper 50 consists of a piston-cylinder assembly whose internal leaks are calibrated.
• the piston 51 is pierced at its center with a calibrated diameter and a ball 53 provided with a spring 54 acting as a non-return valve function, imposes the direction of passage of the oil through the calibrated space 55 between the piston 51 and the cylinder 52.
• a fixed connection via a screw (not shown) is made between the piston 21 and the first attachment 56 of the hydraulic damper 50 and a pivot connection is made by the intermediate axis (not shown) between the second laison 57 of the hydraulic damper 50 and the axis of rotation 27c of a roller 27.
• the rotating assembly 20 is introduced inside the monobloc body 3 and enclosed inside the stator chamber 2 during assembly of the side flanges 6a, 6b.
• the rotary assembly 20 delimits volumetric chambers 35 with the stator enclosure 2.
• a closed oil circuit (not shown) is arranged in the various parts of the rotating assembly 20 to lubricate the contact areas between the different moving parts relative to each other, as is the case axes 25 and 34 respectively ensuring the maintenance of the head 24a and 24b foot rods 24.
• This dry sump circuit comprises an oil pump and an oil reservoir both located outside the stator enclosure 2.
• a heat exchanger is also arranged in the oil circuit to cool it.
• the embodiment consisting in arranging a hydraulic damper 50 between each piston 21 and rollers 27 of the rotary assembly 20 and positioning guide means 7a, 7b in two sectors 71 and 72 able to move in translation. relative to each other does not prohibit the modes of real isation consisting in using only the hydraulic dampers 50 between each piston 21 and rollers 27 of the rotary assembly 20 or that the guide means 7a , 7b.
• the mechanism 1 can be used as a motor to produce a torque on its transmission shaft 40, or as a pump by driving the same transmission shaft 40 with the aid of a coupling connecting it to an external motor.
• one or other of these applications requires arrangements of the one-piece body 3 in order to create intake and exhaust paths for applications of pumps, external combustion engines or engines operating by steam expansion but also ignition for internal combustion engine applications.
• the vertices of the rhombus formed by the four pistons 21 thus follow the path of the inner surface 4 of the one-piece body 3 of the stator enclosure 2 without resting on the same surface 4.
• the segments 31 via the spring 33 present in the segment-carrier device 29 provide a permanent sliding contact on the inner surface 4 of the one-piece body 3 of the stator enclosure 2.
• connection of the segment-carrier device 29 in its notch 28 ensures that the segments 31 have radial contact with the inner surface 4 of the one-piece body 3 of the stator enclosure 2, which makes it possible to reduce their wear and to maintain a good watertightness. volumetric chambers 35.
• the hydraulic dampers 50 arranged on each of the rollers 27 will compensate for this wear at any given moment. making permanent contact between the rollers 27 and the two rolling surfaces 10a and 10b.
• the rolling surfaces 10a and 10b in their embodiment with two sectors 71 and 72 will increase the perimeter of their running surface 10a, 10b to compensate for the wear rollers 27.
• the segment-carrier device 29 may comprise a complementary device for pressurizing the segments 31 on the inner surface 4 of the one-piece body 3 of the stator outer enclosure 2 in order to allow the use of a stator profile of the corresponding and to increase the volumetric ratio between the volumetric chambers 35, and the return device 50 illustrated here by the dampers 50 can be of any type provided that it ensures the contact between the guide means (27, 27a, 27b) and the running surfaces (10a, 10b).

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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)

Applications Claiming Priority (2)

Publications (1)

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• 2009
  • 2009-10-05 FR FR0956912A patent/FR2950926B1/fr not_active Expired - Fee Related
• 2010
  • 2010-10-04 WO PCT/FR2010/052087 patent/WO2011042648A2/fr not_active Ceased
  • 2010-10-04 EP EP10776781A patent/EP2486239A2/de not_active Withdrawn
  • 2010-10-04 US US13/500,219 patent/US20120237370A1/en not_active Abandoned

Non-Patent Citations (1)

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