EP2989294B1 - Volumetrische drehkolbenmaschine mit drei kolben - Google Patents

Volumetrische drehkolbenmaschine mit drei kolben Download PDF

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Publication number
EP2989294B1
EP2989294B1 EP14719756.0A EP14719756A EP2989294B1 EP 2989294 B1 EP2989294 B1 EP 2989294B1 EP 14719756 A EP14719756 A EP 14719756A EP 2989294 B1 EP2989294 B1 EP 2989294B1
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EP
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Prior art keywords
pistons
crankshaft
piston
enclosure
intrados
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EP14719756.0A
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English (en)
French (fr)
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EP2989294A1 (de
Inventor
Jean-Pierre Ambert
Vincent Genissieux
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    • 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
    • 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
    • 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
    • F01C21/08—Rotary pistons
    • F01C21/0809—Construction of vanes or vane holders
    • 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
    • F04C2250/00—Geometry
    • F04C2250/20—Geometry of the rotor

Definitions

  • the present invention relates to a rotating three-piston rotary machine comprising an outer chamber forming a stator in which a rotor is formed consisting of three pistons hinged in their middle on a crank with three branches.
  • the present invention finds a particularly interesting application in the field of combustion engines, turbines, compressors, pumps, hydraulic motors, pneumatic motors, vacuum pumps, and steam engines.
  • rotary deformable diamond machine MRLD
  • deformable diamond rotary machines with four linked pistons have geometrical features which are widely known and disclosed in particular in the patent. FR0805177 (V. GENEssieux ) or in the patent application WO8600370 (Contiero ).
  • the invention aims to provide a rotary machine with three pistons having a power / space ratio and a power / mass ratio more interesting than the three-piston machines of the state of the art, of the order of 2 2.5 times higher, while being more economically advantageous than the four-piston chained machines which have a large number of parts and are more complex to achieve.
  • the subject of the invention is a rotating three-piston rotary machine comprising a stator enclosure in which a rotary rotor assembly comprises a crankshaft cooperating mechanically with the pistons, the rotary assembly defining inside the rotor said chamber six chambers variable volume whose volume varies during the rotation of the rotary assembly, each of the pistons defining with the chamber a variable volume chamber called extrados chamber and two consecutive pistons delimiting with the enclosure and the crankshaft a variable volume chamber called intrados chamber, said machine being characterized in that the geometry of the pistons and the crankshaft is adapted so that each intrados chamber has a cubic capacity equal to or greater than the cubic capacity of the extrados chambers.
  • equal cubic capacity means a cubic capacity equivalent to ⁇ 20%.
  • the rotating machine with three pistons has the advantage of using the internal volume between the pistons so as to form additional sealed chambers, said intrados chambers, by the geometric complementarity of the pistons and the crankshaft which delimits chambers intrados to variable volume during the rotation of the machine, so that this complementarity is dynamic in that the complementary surfaces of the pistons and the crankshaft move away and come closer (until they come in contact when the intrados chamber is at its minimum volume or close to its minimum volume) alternately during the rotation to create this variation in volume of the intrados room.
  • the geometries of the surfaces of the piston and the crankshaft delimiting the intrados chamber, dynamically complementary are linked by a mathematical function of the various geometrical parameters of the machine.
  • the dynamic geometrical complementarity as well as the realization of particular profiles of the pistons and the crankshaft is a sine qua non condition to be able to realize a machine 3 pistons according to the invention of which the intrados rooms have a same working capacity than that of the extrados chambers or a higher displacement, while the engine capacity of the lower chambers of rotary machines with three pistons according to the state of the art are generally of the order of 10% to 20% of the displacement of the extrados chambers.
  • the dynamic geometric complementarity of the pistons and the crankshaft also makes it possible to propose a simple and robust machine by using the principle of direct transmission that can transmit large torques without using a differential system, unlike the four-piston machines connected to one another. known in the state of the art and MRLD machines.
  • the rotary three-piston machine according to the invention makes it possible to produce efficient machines while reducing the number of useful parts, by simplifying them and consequently reducing the cost of producing such a machine with respect to the machines with four connected pistons. .
  • the machine according to the invention has six variable volume chambers which are all capable of performing the various functions of a cycle characterizing the operation of an internal combustion engine, a pneumatic motor, a steam engine, a hydraulic motor, a vacuum pump, a compressor, a pump, etc.
  • the rotary machine with three pistons according to the invention has a very specific internal geometry and different four-piston machines, the pistons having no contact with each other unlike four-piston machines forming a closed kinematic chain, the teaching of Four-piston machines are therefore not directly applicable to rotating machines with three pistons according to the invention having a different internal geometry and whose drive is achieved directly by the complementary geometric shapes between the pistons and the crankshaft.
  • the rotary machine with three pistons also has the advantage of allowing the integration of means for performing additional functions secondary to primary primary functions intrinsic to the operation of the machine without using the intrados or extrados rooms that are usable to perform the primary functions necessary for the main function of the machine.
  • means for performing additional functions secondary to primary primary functions intrinsic to the operation of the machine without using the intrados or extrados rooms that are usable to perform the primary functions necessary for the main function of the machine.
  • such means may be the use of pistons and a capacitive crankshaft.
  • Capacitive means the possibility of temporarily storing and retrieving part of the fluid in transit in the intrados and / or extrados chambers via retractable cavities. In an application where the working fluid is a liquid, this ability can act as a hydraulic anti-lock device.
  • the rotary three-piston machine makes it possible to obtain a displacement of the intrados chamber up to 70% greater than the cubic capacity of the lower chamber of the machine with four connected pistons, and a total displacement per revolution up to 22% greater than the total displacement of a rotary machine with four connected pistons, the two machines having the same ovoid interior profiles of the enclosure.
  • the three-piston MRLD machine according to the invention makes it possible to have a power density, per unit volume or per unit mass, up to 22% greater than the connected four-piston machines of the state of the art.
  • the figure 1 illustrates a sectional view of a first embodiment of the rotary machine with three pistons according to the invention and the figure 2 illustrates an exploded view of the entire machine of this first embodiment.
  • the rotating machine with three pistons 100 comprises a peripheral enclosure 2 forming a stator and defining the receiving enclosure of a mobile assembly 30 forming a rotor and consisting of a central shaft 4 integral or not with a crankshaft 3 cooperating with three pistons 1 .
  • the stator 2 has a generally tubular shape of oval section, whose ovoid profile is preferably in accordance with the geometrical rules imposed in rotating machines with deformable diamond (MRLD). These design rules are in particular known and described in the documents of the state of the art, such as, for example, the patent application FR 2,493,397 to JP AMBERT .
  • the enclosure 2 is closed laterally by two flanges 5a and 5b which may have openings 111 for the circulation of fluids and bearings 103 or bearings at their centers for the rotational guidance of the shaft 4 and / or the crankshaft 3.
  • the crankshaft 3, integral or not with the shaft 4, is indifferently a solid piece or a laminated piece having a width (in the axial direction of the machine, that is to say in the direction of the axis of rotation of the movable assembly 30) substantially equivalent to the width of the enclosure 2.
  • the crankshaft 3 then has a sliding contact with the flanges 5a and 5b during the rotation of the machine 100.
  • the width of the crankshaft may be less than the width of the chamber 2 so that the crankshaft does not have contact with the flanges 5a, 5b.
  • the pistons 1 have a width equal to the width of the enclosure 2, or equal to the width of the crankshaft 3, and are therefore in sliding contact with the flanges 5a and 5b bordering the enclosure 2.
  • Each piston 1 has an outer surface 117 having a cycloidal curvature forming the upper surface of the piston and an inner surface 118 forming the underside of the piston 1.
  • the pistons 1 have two sliding zones 104, symbolized for example by a rupture of the cycloidal curvature of the extrados surface 117. These sliding zones 104 are intended to be in contact with the inner surface of the piston. the chamber 2 and to promote the sealing of the pistons 1 during operation of the machine 100.
  • the sliding zones 104 are formed by sectors of cylinders of revolution 105 forming a break with the extruded cycloid surface 117; the cylinders of revolution 105 and the extrados cycloid surface 117 being tangent.
  • the complete revolution cylinders 105 are shown in dashed lines at the figure 1 for better visibility.
  • the cylinders of revolution 105 forming these sliding zones 104 may have more or less significant diameters, including zero diameters, thus forming more or less large slip zones 104 which will be adapted according to the needs, characteristics and characteristics. architecture of the rotary machine 100.
  • the pistons 1 and the crankshaft 3 cooperate together by means of a pivot connection 106 adapted to allow the tilting and rotation of the pistons 1 in the chamber 2, whose inner profile is advantageously a MRLD type profile, to allow the surface of the underside to come to marry the complementary surface of the crankshaft 3, and to allow the transmission of a torque of the pistons 1 to the crankshaft 3 or vice versa.
  • a pivot connection 106 adapted to allow the tilting and rotation of the pistons 1 in the chamber 2, whose inner profile is advantageously a MRLD type profile, to allow the surface of the underside to come to marry the complementary surface of the crankshaft 3, and to allow the transmission of a torque of the pistons 1 to the crankshaft 3 or vice versa.
  • the pivot connection 106 forms a tilting means consisting of a tilting cylinder 107 (convex male portion of the pivot connection 106) in the middle of the intrados surface 118 of the pistons 1 cooperating with a tilting cup 127 having a concave shape complementary of the tilting cylinder 107 (female part of the pivot connection 106), arranged in the crankshaft 3, the tilting of the tilting cylinder 107 in the tilting bowl 127 allowing the rotation of the pistons 1 in the chamber 2 and the alternative tilting pistons 1 relative to the crankshaft 3 around the pivot connection 106 thus ensuring the volume variation of the intrados chambers 102.
  • the tilting cylinder 107 is extended at least over part of the width of the crankshaft 3 as visible on the figure 2 .
  • the contact surface between the tilting cylinder 107 and the tilting cup 127 extends over an angular sector sufficient to prevent the tilting cylinder 107 from coming out of the tilting pan 127, which would cause the piston 1 to jam between the enclosure 2 and the crankshaft 3.
  • This sufficient angular sector is directly dependent on the mathematical parameters of the ovoid of the enclosure 2, those of the intrados surface 118 and those of the outer surface of the crankshaft 3.
  • bearings can advantageously be housed in the male parts of the tilting cylinder 107 or in the female parts thereof, such as for example plain bearings or any other means of type rolling bearing adapted to support this reciprocating tilt movement and able to withstand the phenomenon of contact wear and fretting (wear in the case of an oscillating movement contact of small amplitude).
  • the tilting cylinder 207 ie the male part of the pivot connection 206
  • the concave tilting bowl 227 ie the female part of the pivot connection 206
  • the female part and the male part has a contact area of more than half a section of the tilting cylinder, ie greater than 180 °. This important contact zone advantageously allows the recovery of the centrifugal force of the piston 1 by the crankshaft 3.
  • the tilting cylinder 207 may be an element attached to the crankshaft 3 or on the lower surface of the piston 1, in order to simplify the manufacturing range of such a machine and to lower the cost of production of the parts.
  • the tilting cylinder is a part independent of the crankshaft 3 and pistons 1.
  • the tilting cylinder cooperates with two bowls tilt concaves arranged on both the crankshaft 3 and the pistons 1.
  • the transmission of the movement between the crankshaft 3 and the pistons 1 is ensured by a tangential force transmitted between the female part and the male part of the pivot connection 106, 206, the direction of transmission of the tangential force depending on the variant embodiment. the pivot connection 106, 206 but also the direction of transmission of the rotational torque, that is to say the pistons 1 to the crankshaft 3 or vice versa.
  • the pivot connection is formed by a hinge connection 306 having tilting cylinders 307 alternately arranged on the crankshaft 3 and on the pistons 1, cooperating with tilting cuvettes 317, the assembly being held by an axis 10 passing through the different cylinders
  • the tilting and the transmission of the forces are carried out by the axis 10 of the hinge 306 which also serves to take up the centrifugal force applied to the pistons 1.
  • this pivot connection 106 can be made by means of a material having a low coefficient of friction and optionally with a surface treatment. It is also envisaged to limit the friction of the pivot connection 106, 206, 306 by the use of suitable rolling components, such as for example plain bearings, ball bearings or needle bearings. It is also envisaged to limit the friction of the contact zone of the pivot connection 106, 206, 306 by creating a hydrodynamic or aerodynamic film. This thin hydrodynamic film is produced by integrating a portion of the compressed fluid flow between the male part and the female part of the pivot connection 106, 206, 306 so as to promote sliding during tilting.
  • the pivot connection 406 is formed by one or more flexible parts having a generally blade shape extending over at least part of the length of the crankshaft 3 and / or pistons 1.
  • These flexible blades 15 are positioned in two grooves 131, 132 arranged in a direction parallel to the axis of tilting of the pivot connection 406, respectively in the pistons 1 and in the crankshaft 3.
  • the flexible blades 15 can be made by a superposition of flexible thin blades, or by the use of a flexible plastic material, such as an elastomer, having mechanical characteristics to advantageously withstand the phenomenon of fatigue.
  • the flexible part can also present a specific reinforcement having a section adapted to improve the fatigue strength of the flexible part, such as for example an X-shaped section.
  • Such a flexible blade is for example mounted compressed in the grooves 131, 132, which allows, by elastic return of the blade, to exert a radial force capable of improving the sealing of the piston / chamber contacts.
  • Such a flexible blade 15 also makes it possible to improve the seal between each intrados chamber 102 of the machine 100.
  • the flexible blades 15 thus provide the function of pivoting, torque transmission and sealing of the machine. link.
  • the upper surface 117 of the pistons defines with the inner wall of the chamber 2 and the flanges 5a, 5b three outer chambers 101, said extrados chambers, forming cavities with variable volume whose volume varies between a maximum volume and a minimum volume during relative movement of the rotor 30 relative to the stator 2; this minimum volume may be at the zero limit according to the mathematical parameters of the ovoid of the enclosure 2 and those of the extrados surface 117.
  • the rotary machine 100 also comprises three chambers 102, said intrados chambers, each intrados chamber 102 being interposed between two extrados chambers 101.
  • the intrados chambers 102 are delimited by the intrados faces 118 of two consecutive pistons 1, by the lateral faces 115 and by the faces of the cylinders of revolution 105 of the pistons 1 forming a junction surface between the extrados surface 117 and the intrados surface 118 of the pistons 1, the inner wall of the enclosure 2, the crankshaft 3 and the flanges 5a, 5b .
  • the intrados chambers 102 also form cavities of variable volume whose volume varies between a maximum volume and a minimum volume during the relative movement of the rotor 30 with respect to the enclosure 2, this volume variation being advantageously due to the reciprocating tilting movement of the pistons 1 relative to the crankshaft 3 around the pivot connection 106 so that the complementary surfaces of the crankshaft 3 and the piston 1 (formed by the intrados surface 118, the cylinders of revolution 105, and the lateral faces 115) move away and approach each other alternately.
  • the crankshaft 3 has a circular section.
  • the crankshaft may also have a triangular section as illustrated in FIGS. Figures 7 and 8 , a curvilinear triangular section as illustrated in Figures 5 and 6 , or a hexagonal section as illustrated in Figures 9 and 10 .
  • the associated pistons obviously have a complementary intrados profile of the outer surface of the crankshaft. It is understood that variants of the pivot connection 106 between the pistons 1 and the crankshaft 3 described above are applicable irrespective of the profile of the crankshaft 3.
  • the pistons 1 may comprise skirts 17 fixed on their lateral flanks, such a variant is illustrated in FIG. figure 15 .
  • the skirts 17 are for example elements attached to the pistons 1 whose profile adopts that of the extrados face 117 of the piston 1 for the upper part and a circular profile or other for the lower part.
  • the profile of the lower part and the thickness of the skirts 17 are defined according to the application and the profile of the piston 1 so as not to interfere with the transmission shaft 4.
  • the skirts 17 flanked on the pistons 1 have for the advantage of stiffening the piston especially when the cylinders of revolution 105 forming the sliding zones 104 of the extrados surface 117 have a small radius, or when the radial thickness of the piston 1 is small compared to the pressures exerted by the fluid in the chambers 101, 102.
  • the skirts 17 also make it possible to adjust the admissions and axial discharges of the fluids operated through the openings 111 in the flanges 5a, 5b.
  • the circulation of the fluids in the chamber 2, and more precisely in the cavities formed by the intrados 102 and extrados 101 chambers, is made by one or more axial openings 111 made in one or in the two lateral flanges 5a, 5b and / or by one or more radial openings (not shown) made in the chamber 2 or in the crankshaft 3.
  • the axial openings 111 can communicate only with the intrados chambers 102, likewise for the radial openings in the crankshaft 3.
  • the rotary machine 100 does not require the use of valve or valve for admissions and repressions, the pistons 1, with or without skirts 17, and / or the crankshaft 3 obstructing and alternatively discovering the axial openings 111 and radial when of their rotation.
  • the shape, the section, the number, as well as the locations of the openings allowing the entry and the exit of fluids being defined according to the operating characteristics of the rotary machine 100.
  • the openings are thus parameterized according to the application, fluid and desired characteristics.
  • the three-piston rotary machine 100 has six cavities of variable volume formed by the three intrados chambers 102 and the three extrados chambers 101.
  • Each intrados chamber 102 is diametrically opposed to an extrados chamber 101 and their volume variations (increase or decrease) are synchronous.
  • the particular arrangement of the pistons 1 and the crankshaft 3 presented above as well as the dimensions of the pistons 1 and the crankshaft 3 advantageously defined enable a rotary machine with three pistons 100 having intrados chambers 102 and extrados chambers with displacements and / or compression ratios equal to ⁇ 20%, or greater than the displacements and / or compression ratio of the extrados chambers 101.
  • the production of six cavities with variable volume having the same or substantially the same displacement makes it possible to produce machines operating primary primary functions in each of these six chambers, with a power / space ratio and a power / mass ratio that are very interesting for various applications. conventional three-piston or chained four-piston machines can not reproduce.
  • the displacement of the intrados chamber 102 can be up to 50% greater than the displacement of the extrados chamber 101.
  • such a machine can advantageously be used in combustion internal combustion engine, hydraulic motor, pneumatic motor, steam engine (s), pump, vacuum pump or compressor mode mode, each of the variable volume cavities thus corresponding to a particular state according to a mode of use of the machine.
  • the same 3-piston volume machine according to the invention can combine several different modes of use within its six intrados and extrados chambers, simultaneously or successively, and advantageously up to 4 different modes of use, such as for example: a mode of use in a compressor in the extrados chambers 101 and a mode of use in expansion motor in the intrados rooms 102, or a mode of use in hydraulic pump in the intrados chambers operating in the right side of the machine and a method of using a hydraulic motor in the intrados chambers 102 operating in the left side of the machine.
  • the Figures 18 to 29 illustrate different positions of the rotating machine at different angles of rotation of the pistons A, B and C and the crankshaft with a pitch of 30 ° between each figure.
  • the figure 18 illustrates the position of the pistons A, B, C in a so-called reference position, that is to say at the angle 0 °
  • the figure 19 illustrates the position of the pistons A, B, C with a 30 ° rotation in the clockwise direction relative to the position of the pistons of the figure 18
  • the figure 20 illustrates the position of the pistons A, B, C with a rotation of 60 ° with respect to the position of the pistons A, B, C of the figure 18 and so on until the figure 29 which represents the position of the pistons A, B, C with a rotation of 330 ° with respect to the position of the pistons A, B, C illustrated in FIG. figure 18 .
  • All of the Figures 18 to 29 therefore illustrates twelve positions of the pistons A, B, C for a crankshaft revolution.
  • the figure 30 represents in the form of a table, the different main functions performed by the various variable volume cavities of the machine according to their position in the chamber during a crankshaft revolution when the machine is used in thermal engine mode to internal combustion.
  • the figure 31 also illustrates in the form of a table, the different main functions performed by the different variable volume cavities of the machine according to their position in the chamber during a crankshaft revolution when the machine is used in pneumatic motor mode or steam engine or hydraulic motor.
  • the rotary machine with three pistons 100 has the advantage of having no dead point, that is to say that each motor-generating time of movement occupies a quarter turn (ie 90 °) of the machine, each rotor position has at least one engine time as illustrated in the Figures 30 and 31 . It should be noted that ( figure 31 ), for operation in pneumatic motor mode or steam engine or hydraulic motor, the driving time of a lower chamber 102 is synchronous with the driving time of the extrados chamber 101 opposite to the axis of rotation of the machine.
  • the intrados chambers 102 may have a dead volume which is defined by the volume between two pistons 1, the chamber 2 and the crankshaft 3 when the pistons 1 are at the closest, symmetrical with respect to a passing radial plane. by the axis of rotation of the machine.
  • the dead volume corresponds to the geometric volume of the cavity when it is at its minimum volume at the end of the exhaust, this geometric volume may therefore contain a residual volume of the working fluid. Thanks to the specific geometry of the pistons 1 and the crankshaft 3, the dead volume of the intrados chambers 102 is important to 100% of the cubic capacity of the intrados chamber 102, or very low and less than 5%.
  • the dead volume can be further minimized by changing the geometry of the side faces 115 of the pistons 1 and / or by minimizing the diameter of the revolution cylinders 105 forming the sliding zones 104.
  • An example of minimizing the dead volume is illustrated at Figures 32 and 33 by changing the geometry of the pistons, the figure 32 illustrating the residual dead volume of an intrados chamber 102 without optimization and the figure 33 illustrating the residual dead volume for the same intrados chamber 102 with optimization.
  • Such optimization makes it possible to go from a dead volume of 4% of the displacement of the intrados chamber 102 to a dead volume of less than 0.5% of the cubic capacity, and advantageously a theoretical dead volume equal to 0, and to multiply by example a theoretical compression ratio by 4, up to a value of 150 and without significantly changing the cubic capacity of the cavities 102, this displacement after optimization of the dead volume having varied only 0.2%, and according to section profiles of the crankshaft 3 this displacement of the intrados chamber 102 may be exactly the same before and after optimization of the reduction of the dead volume of said intrados chamber 102.
  • the reduction of this dead volume of the intrados chamber 102 sets implementing mathematical functions involving the geometrical parameters of the machine 100 according to the invention, especially concerning the lateral faces 115 and the joining surfaces between these these lateral 115 and, on one side the intrados face 118, on the other side the extrados face 117.
  • the rotary machine according to the invention makes it possible, for example, to produce an engine pneumatic or steam engine having a power equal to or greater than 3000 Watts at 1000 revolutions per minute at a pressure of 10 bars relative to a small bulk (including an overheating prechamber located outside enclosure 2): 14 , 5 cm long, 11.2 cm wide and 10 cm high for a total displacement of 360 cm3 (cm 3 ), and therefore an admitted geometric volume of 720 cm3 per revolution of crankshaft.
  • the theoretical gross engine torque (ie excluding mechanical and hydraulic losses) of this steam engine according to the invention illustrated in FIG.
  • figure 45 varies between 61 and 85 Newtons.meter (Nm), and its average gross torque on a lap is 78 Nm
  • a double-acting alternating steam engine of total displacement identical to that of the 3-piston machine according to the The invention has a theoretical average gross torque of 57 Nm, 27% lower, for a much larger bulk and mass.
  • the figure 46 illustrates the theoretical gross engine torque, on a crankshaft revolution, as well as the average torque of various rotary machines known from the state of the art (four-piston MRLD machine, rotary double-acting rotary machine).
  • a rotary machine of the MRLD type with 4 extrados chambers, of the same dimensions, of the same external dimensions and of the same ovoid interior profile of the enclosure has a mean theoretical torque of 69.5 Nm, ie 10, 9% lower than that of the machine according to the invention.
  • the rotary machine according to the invention can be used to produce a micro-pump, and advantageously a dosing micro-pump when the intrados and extrados chambers have an identical capacity.
  • a metering micro-pump may have a total cubic capacity of 0.907 cm 3 per revolution (or 907 microliters per revolution) for a space volume of 6.3 cm 3 .
  • the total cubic capacity can advantageously be increased to more than 1.1 cm 3 per revolution, with in this case a cubic capacity of the intrados chamber 41% greater than the displacement of the extrados chamber, and this for the same reduced size: an outer diameter of 20 mm for an axial length of 20 mm.
  • the theoretical dead volume of the extrados chamber is zero, and that of the intrados chamber is less than 0.35% of the cubic capacity of the intrados chamber, ie a theoretical compression ratio of the intrados chamber of 290.
  • Such a micro-pump made of a suitable steel, has a mass of about 50 grams, and allows a pressure difference of greater than 20 bars for the larger displacement variant, greater than 100 bars for the micro-dosing variant. .
  • Such a micro-pump can operate at rotational speeds greater than 1000 revolutions per minute, and develops a hydraulic power of compression of the order of 36 Watt at 1000 revolutions per minute for a pressure differential of 20 bar.
  • the machine according to the invention may be a wheel motor in which the crankshaft 3 is fixed in rotation and the chamber 2, constituting the wheel, rotates.
  • the supply and the discharge of the fluids in this wheel motor is simple since axial by the shaft 4 and the crankshaft 3 which in this case are fixed in rotation, then by the cylinder (s) and bowl (s) of tipping via specially designed channels to access the extrados rooms.
  • the rotating machine with three pistons according to the invention advantageously has pistons, a crankshaft and a solid enclosure.
  • This particular feature allows the pistons, the crankshaft and the enclosure to be able to include means capable of providing additional functions secondary to the main primary functions corresponding to the operating states of the machine in its various possible modes of use: heat engine internal combustion engine, hydraulic motor, pneumatic motor, steam engine (s), pump, compressor, vacuum pump or a combination of its modes.
  • heat engine internal combustion engine hydraulic motor, pneumatic motor, steam engine (s), pump, compressor, vacuum pump or a combination of its modes.
  • these means may be a system performing a hydraulic anti-lock function to prevent the mechanism from locking due to the property of non-compressibility of liquids, during a hydraulic application of the machine according to the invention.
  • This first exemplary embodiment is illustrated in Figures 34 to 36 .
  • the pistons 1, and / or the crankshaft 3, and / or the enclosure 2 have retractable volumes 24 which make it possible to increase the volume, and consequently the displacement, of the intrados chambers 102 and / or extrados 101.
  • These retractable volumes are formed by axial or radial cavities 20 in which slide one or pistons 18 pushed by springs 19, or by any other component able to exert a thrust force, which are dimensioned according to the desired behavior.
  • An embodiment of this anti-lock system is illustrated on the crankshaft 3 to Figures 35 and 36 .
  • this system is also transferable to the pistons 1, intrados side 118 and / or extrados side 117, and the enclosure 2.
  • the figure 43 is a sectional view, according to the cutting plane AA defined at the figure 42 of the deformation of the flexible and impermeable membrane 25 when the pressure P1 in the intrados chamber 102 is greater than the pressure P2 present in the closed cavity 20.
  • the plate which holds the membrane 25 in place and clamped against the crankshaft 3 can be advantageously a grid, visible on the figure 44 , so that the membrane 25 does not deform inside the chamber 102 when the pressure P1 is less than the pressure P2, for example where the chamber 102 is at the inlet and therefore undergoes a possible depression.
  • One of the major advantages of this variant design of cavities 20 through a membrane 25 is its total sealing.
  • these volumes retractable waterproof 24 remain fully operational in their function.
  • the fluid present in the closed cavity 20 may be a gas or a liquid depending on the function assigned to this retractable volume, which is identical to or different from the working fluid in the intrados and / or extrados chambers; its pressure can be regulated by a complementary device internal or external to the machine 100.
  • this system detailed here for the case of retractable volumes 24 in the crankshaft 3, is also adaptable to the pistons 1, intrados side 118 and / or extrados side 117, and on the enclosure 2.
  • the means capable of providing an additional function to the machine may be electromechanical or magnetic components adapted to allow the transmission of torque between the rotary assembly 30 and a rotating shaft outside the machine. (or conversely) so that the chambers of the machine can be completely sealed with respect to the external environment of the machine.
  • Said electromechanical or magnetic components are advantageously housed in the crankshaft 3 or in the pistons 1 and cooperate, through a sealed and nonmagnetic wall, with other electromechanical or magnetic components housed either in the side walls 5a, 5b of the machine, or outside of these, either in the rotation shaft 4 of the machine passing through the crankshaft 3 by its center and not integral with it.
  • the means capable of providing an additional function secondary to the machine can make it possible to improve the trajectory of the input flows (intake flows) and of the output flows (exhaust flows) as well as to regulate the flows in the intrados chambers 102.
  • the means are formed by cylindrical or conical axial notches in the crankshaft 3.
  • the figure 16 illustrates for this purpose an embodiment of a crankshaft 3 having conical axial slots 114; the base of the cone of the notch 114 being oriented towards the axial openings 111 of the flanges 5a, 5b.
  • the means capable of providing an additional function secondary to the machine may make it possible to improve the trajectory of the input flows (intake flows) and of the output streams (exhaust flows) as well as to regulate the flows in the extrados chambers 101.
  • the means are formed by notches in the flanks of the pistons 1.
  • the figure 17 illustrates for this purpose an embodiment of the interior of a rotary machine 100 according to the invention having pistons 1 with notches 121 on the sidewalls 116 forming a passage between the sidewalls 116 and the upper surface 117.
  • the notches 121 can also be replaced by a channel arranged in each piston connecting the upper surface 117 to one or both sides 116 of the piston 1, thereby communicating the passage axial windows 111 of the flanges 5a, 5b with the extrados chambers 101.
  • sealing means may be conventional sealing means commonly used in rotary machines with three pistons or in rotating machines with deformable rhombus.
  • the figure 37 illustrates a piston having at its extrados surface 117 a first embodiment of a sealing means.
  • the seal is made by a cylindrical seal 13 positioned in a cylindrical groove in the piston 1.
  • the cylindrical groove formed in the piston 1 substantially corresponds to the dimensions of the revolution cylinders 105 described above forming the zone sliding piston 104 1.
  • the cylindrical seal 13 is pivotally connected to the piston 1 so as to allow its rotation in the cylindrical groove; the use of combinations of materials and / or surface treatments with appropriate tribological properties makes it possible on the one hand to reduce the friction losses of said pivot connection of the cylindrical seal 13 in the piston 1, and on the other hand to ensure the adhesion of the cylindrical seal 13 against the ovoid surface of the enclosure 2.
  • An improvement of this first embodiment of a sealing means consists in mounting the axis of the cylindrical seal 13 on components of bearing of suitable dimensions, such as ball bearings, needle bearings or plain bearings, said support bearing components of the axis of the seal 13 being housed in the piston 1 so that they can have a controlled radial movement thus making it possible to compensate for the wear play between the cylindrical seal 13 and the enclosure 2.
  • the cylindrical seal 13 rolls on the ovoid surface of the enclosure 2 limiting its wear and losses mechanical.
  • the diameter of the cylindrical seal 13 is carefully calculated from the parameters mathematics of the machine 100 so that it is fully contained in the end of the piston 1 and that the thickness of material between its housing and the side face 115 is sufficient to ensure the necessary mechanical strength.
  • Such an alternative embodiment of the rolling contact sealing makes it possible, in relation to the sealing means of the state of the art, firstly to significantly reduce the mechanical losses in friction between the seal and the enclosure and by therefore, to improve the efficiency of the machine, and secondly to make up for the wear of the seal and consequently to increase the service life of this sealing part.
  • the figure 40 illustrates a piston having at its extrados surface 117 an alternative of the second alternative embodiment of a sealing means described above.
  • the seal is made by a segment 11 pushed against the inner ovoid surface of the chamber 2 by the pressure of the fluid of the intrados and / or extrados chambers.
  • the segment 11 is formed by a bar of rectangular section, one of whose sides has a rounded shape and radius equivalent to the radius of the revolution cylinder 105 of the sliding zone 104. This rounded face allows the piston 1 to move along the enclosure 2.
  • the segment 11 is housed in an axial groove of the piston 1 and is pushed by hydraulic or pneumatic pressure radially towards the chamber 2.
  • Channels 108 and 109 are arranged in the piston 1 so as to connect the axial groove respectively to the intrados chamber 102 and to the extrados chamber 101 of the machine and to allow the arrival of fluid under the segment 11 to exert a radial pressure on the segment 11 which in turn exerts pressure on the inner surface ovoid of the chamber 2 to achieve the seal.
  • This third embodiment may further include a system of valves constituted, for example, by sealing balls of the channels 108 and 109 enclosing the fluid under pressure in the thrust chamber of the segment 11 at the axial groove. Such a system ensures a contact pressure of the segment 11 on the inner surface of the chamber 2 just sufficient to seal, it also allows a recovery of the wear clearance.
  • the Figures 47 and 48 illustrate a fourth variant embodiment of an axial dynamic sealing means between the two flanges 5a and 5b and the parts of the rotary assembly 30, namely the pistons 1 and the crankshaft 3.
  • the figure 47 is an exploded perspective view of the machine 100 for which the openings 111 for the circulation of working fluid, illustrated in FIG. figure 2 , are divided into intake windows 112 formed in the first flange 5a, and discharge windows 113 formed in the second flange 5b.
  • the flange 5b is integral with the stator 2 (shown only on the figure 48 ).
  • a third flange 119 also integral with the stator 2, is positioned in front of the intake flange 5a, opposite side to the chambers, so that an inlet prechamber 125 is created between the two flanges 119 and 5a.
  • the flange 5a is slid inside the stator 2 in the axial direction of the machine, and has on its periphery a first groove for receiving a peripheral seal 123, and a second groove, formed inside the cylindrical passage of the shaft 4, intended to receive a shaft seal 127.
  • the seals 123, 127 ensure the sealing between the chambers, extrados 101 and intrados 102, and the pre-admission chamber 125.
  • the extrados 101 and intrados 102 chambers operate a relaxation of the working fluid. Consequently, the pressure, called P1, corresponding to the pressure of the working fluid upstream of the inlet windows 112 is greater than or equal to the pressure, called P2, of the same working fluid in the intrados chambers 102 and extrados 101 of the machine, in the phase of relaxation then of repression.
  • the inlet prechamber 125 remains continuously under maximum pressure P1, that is to say that of the working fluid at the inlet into the machine via the general intake manifold 129.
  • P1 maximum pressure
  • This constant pressure in the prechamber 125 ensures a thrust of the intake flange 5a against the rotor 30, and a thrust of the rotor 30 against the discharge flange 5b, thereby perfecting the dynamic seal by plane-plane contacts without play and the catch of the wear clearance between the pistons 1 and crankshaft 3 on the one hand and puddles 5a, 5b on the other hand.
  • the intake flange 5a also has orifices 124, allowing the working fluid present in the prechamber 125, under maximum pressure P1, to access the bottom of the two grooves of the flange 5a, ie at the bottom of the peripheral groove and the throat shaft, in order to exert a thrust of the peripheral seal 123 against the ovoid inner surface of the stator 2 and a thrust of the shaft seal 127 against the shaft 4.
  • this sealing means may also be completed by a counter-thrust actuator 126 , preferably housed in the crankshaft 3.
  • this counter-thrust actuator 126 may be embodied by two springs properly sized according to the application surfaces of the pressures P1 and P2 on each side of the flange 5a and the characteristics of the expansion cycle in the chambers 101, 102 so as to to minimize the contact pressures in the axial stack formed by the flange 5a, the pistons 1, the crankshaft 3 and the flange 5b.
  • the counter-thrust force of this actuator 126 may be variable depending on the angle of rotation and the time so that the resulting force of the counter-thrust force of the actuator 126 added to the force pushing against the flange 5a of the working fluid under pressure P2 in the chambers extrados 101 and intrados 102, is continuously equivalent (and in the opposite direction) to the pushing force against the flange 5a of the working fluid under pressure P1 in the prechamber 125.
  • the contact pressures exerted between the flat surfaces flanges 5a, 5b and parts of the rotor 30 are very low or zero.
  • this dynamic sealing means can be completed by fine grooves, made either on the faces of the flanges 5a, 5b located on the chamber side 101, 102 or on the lateral flanks of the pistons 1 and the crankshaft 3. These thin grooves thus play. the role of labyrinthine joints 156 (not visible on the Figures 47 and 48 ).
  • This improvement of the dynamic seal can also be obtained by texturing the same antagonist faces of these same parts, in the form of micro-cells in which a vortex effect is created at the origin of an aerodynamic lift between the two opposing faces. relative motion.
  • This fourth embodiment of a dynamic sealing means is applicable following the same principles when the machine 100 is used in compressor, or hydraulic pump, or vacuum pump.
  • the third flange 119 is placed after the flange 5b comprising the discharge windows 113, opposite side to said intrados and extrados chambers, forming with the latter a post-discharge chamber.
  • the intake flange 5a is integral with the stator 2 and the flange 5b is axially slidable in the stator 2.
  • This fourth embodiment of a dynamic sealing means is applicable according to the same principles when the machine 100 comprises radial working fluid circulation openings, that is to say radially formed in the chamber 2 and / or in the crankshaft 3, to access the intrados chambers 102 and / or extrados 101. Then, the 3 flanges 5a, 5b and 119 are blind and the prechamber 125, or the postchambre, is filled with the pressurized working fluid upstream, respectively downstream of said radial openings.
  • the Figures 49 to 51 illustrate a fifth variant embodiment of a dynamic sealing means of the rotary machine.
  • the sealing means makes it possible to achieve axial and radial sealing.
  • the axial seal is formed between the two flanges 5a and 5b and the parts of the rotary assembly 30, namely the pistons 1 and the crankshaft 3, and the radial seal is formed between the piston 1 and the stator 2 via the contact of a cylindrical seal 13 rolling against the ovoid inner surface of the stator 2 during the rotation of the rotary assembly 30.
  • the general principle of this fifth variant rests on the implementation of aerostatic bearings, thanks to the use of a pressurized operating fluid injected into the flanges 5a, 5b and inside the parts constituting the rotor 30.
  • service fluid can be indifferently a gas or a liquid under pressure, in this second case the bearings are called hydrostatic.
  • the pressurized operating fluid used to feed these aerostatic bearings is the working fluid of the main function of the machine provided in the extrados chambers 101 and / or intrados 102.
  • the machine 100 is a compressor or a pump, part of the flow of the working fluid under pressure is diverted from a post-chamber downstream of the discharge windows 113.
  • the figures 50 and 51 are respectively axial and radial sections of the rotary machine 100 having a dynamic sealing means according to this fifth embodiment.
  • the figures 50 and 51 illustrate more particularly the different channels and grooves conveying the operating fluid under pressure from a post-chamber (not shown) located downstream of the discharge windows 113 to the various aerostatic bearings used in the rotor 30 and the flanges 5a, 5b.
  • these aerostatic bearings consist either of a pressurized fluid pocket in one of the two antagonistic parts of the sliding contact, as illustrated at the pivot connection 106, aerostatic pocket whose opening dimensions are calculated according to the lift pressure sought between the opposing surfaces, either by porous micro-cellular materials.
  • These materials have the advantage of creating a very uniform pressure field over their entire diffusion surface of the pressurized operating fluid and, in the case of the contacts listed above, the formation of a thin film of said service fluid in the mechanical clearance existing between the opposing surfaces in relative motion relative to each other. As a result, the two opposing surfaces slide on this pressurized service fluid film.
  • This fluid film operates a lift effect of the opposing surfaces that are no longer touching, and thus ensures their dynamic sealing with an extremely low coefficient of friction, depending on the viscosity of the used operating fluid (of the order of 0.00001 when this service fluid is air).
  • Other mechanical solutions for these aerostatic or hydrostatic bearings can be implemented as alternatives to the two examples of solutions described above and illustrated in this fifth variant of dynamic sealing means.
  • the pressurized operating fluid passes through the discharge flange 5b via an axial channel 141. It fills the circular groove 142 to allow continuous diffusion in the axial channels 144 crankshaft 3 in rotation relative to the flange 5b.
  • the service fluid is also propagated to the aerostatic shaft bearing 152 and the annular aerostatic bearing 151 via the radial channels 143 formed in the flange 5b. From the axial channels 144 of the crankshaft 3, the pressurized operating fluid gains on the one hand the other flange 5a for supplying the two other aerostatic bearings 151,152, and on the other hand the pivot connection 106 via the radial channels 145 of the crankshaft 3.
  • the access channels of the pressurized operating fluid inside the crankshaft 3 can also be made in the rotation shaft 4 of the machine.
  • the pressurized operating fluid fills the aerostatic bearing bag 155 formed in the tilting bowl 127 and whose pressure force is exerted against the tilting cylinder 107, bearing it .
  • the width of this aerostatic ball bearing 155 in the radial plane is calculated so that the continuity of the distribution of the operating fluid between the radial channel 145 of the crankshaft 3 and the radial channel 146 of the piston 1 is ensured whatever the position of the piston 1 during the rotation of the rotor 30.
  • the pressurized operating fluid is conveyed to the planar aerostatic bearings 153 and the semi-cylindrical aerostatic bearings 154 via the terminal channels axial 147 and radial end channels 148.
  • the sintering process of the powders may be particularly suitable for producing such solid porous pistons 1, followed by a calibration operation to obtain the desired dimensional and geometrical accuracies, and then a surface treatment to seal the faces of the piston 1 not intended to have an aerostatic bearing function, it is ie those defining the extrados 101 and intrados 102 chambers.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Hydraulic Motors (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Claims (14)

  1. Volumetrische Drehkolbenmaschine (100), umfassend:
    • ein röhrenförmiges Gehäuse (2) mit ovalem Querschnitt;
    • eine in dem Gehäuse rotatorisch angebrachte Kurbelwelle (3), und
    • drei Kolben (1) in dem Gehäuse, die jeweils in deren Mitte an der Kurbelwelle angelenkt und so konfiguriert sind, dass sie zwei entgegengesetzte Enden (104) in ständigem Kontakt mit dem Gehäuse haben, wenn sich die Kurbelwelle in Bezug auf das Gehäuse dreht, woraus sich ergibt, dass jeder Kolben altenierend um seine Anlenkung an der Kurbelwelle gekippt wird;
    dadurch gekennzeichnet, dass jeder Kolben zwei Innenflächen hat, die sich radial auf jeder Seite der entsprechenden Anlenkung an der Kurbelwelle erstrecken, wobei jede Innenfläche ein Profil aufweist, das zu dem Profil der Außenfläche der Kurbelwelle komplementär ist, so dass der Kolben imstande ist, sich an die Form der Kurbelwelle nach einem Prinzip der alternierenden Annäherung und Beabstandung während des Kippens anzuschmiegen.
  2. Volumetrische Drehkolbenmaschine nach Anspruch 1, wobei jeder der Kolben (1) mit dem Gehäuse (2) eine Kammer mit veränderlichem Volumen, bezeichnet als Außenkammer (101), begrenzt und zwei aufeinanderfolgende Kolben (1) mit dem Gehäuse (2) und der Kurbelwelle (3) eine Kammer mit veränderlichem Volumen, bezeichnet als Innenkammer (102), begrenzen, wobei die Kolben (1) und die Kurbelwelle (3) derart konfiguriert sind, dass jede Innenkammer (102) einen Hubraum aufweist, der gleich oder größer als der Hubraum der Außenkammern (101) ist.
  3. Volumetrische Drehkolbenmaschine (100) nach Anspruch 1, wobei das Gehäuse (2) ein Profil in Übereinstimmung mit den geometrischen Regeln aufweist, die in Drehkolbenmaschinen mit verformbarem Rhombus gelten.
  4. Volumetrische Drehkolbenmaschine (100) nach Anspruch 1, wobei die Anlenkung (406) jedes Kolbens an der Kurbelwelle ein flexibles Element (15) aufweist, das in Nuten (131, 132) der Kurbelwelle (3) und des Kolbens (1) eingebettet ist.
  5. Volumetrische Drehkolbenmaschine (100) nach Anspruch 1, umfassend:
    • zwei Flansche (5a, 5b), die das Gehäuse seitlich verschließen; und
    • aerostatische oder hydrostatische Lager (151, 152, 153, 154, 155), die konfiguriert sind, um eine radiale dynamische Dichtung zwischen den Kolben (1) und dem Gehäuse (2) und eine axiale dynamische Dichtung zwischen den Flanschen (5a, 5b) und der Kolben-Kurbelwellenanordnung (30) bereitzustellen,
    wobei die Lager so konfiguriert sind, dass sie von dem Betriebsfluid der Maschine versorgt werden.
  6. Volumetrische Drehkolbenmaschine nach Anspruch 1, umfassend:
    • zwei Flansche (5a, 5b), die das Gehäuse (2) seitlich verschließen und Öffnungen (111) zum Einlassen und Auslassen von Fluiden in durch die Kolben definierte Kammern (102, 101) mit veränderlichem Volumen aufweisen; und
    • eine radiale Kerbe (121) in einer Seitenflanke jedes Kolbens (1), die einer oder mehreren der Öffnungen (111) der Flansche (5a, 5b) zugewandt angeordnet ist.
  7. Volumetrische Drehkolbenmaschine nach Anspruch 6, wobei jeder Kolben (1) eine dem Gehäuse (2) zugewandte Außenfläche (117) und einen inneren Kanal aufweist, der die Außenfläche (117) mit der Kerbe in der Seitenflanke verbindet.
  8. Volumetrische Drehkolbenmaschine nach Anspruch 1, umfassend Rotationsdichtungen (13) in jedem Kolben, die imstande sind, während der Rotation der Kolben (1) auf dem Gehäuse zu rollen.
  9. Volumetrische Drehkolbenmaschine nach Anspruch 1, umfassend in jedem Kolben einstellbare Dichtungen (14, 11), deren Anpressdruck an das Gehäuse (2) in Abhängigkeit von dem Druck in volumenvariablen Kammern (102, 101), die von den Kolben definiert sind, einstellbar ist.
  10. Volumetrische Drehkolbenmaschine nach Anspruch 1, umfassend:
    • zwei Endflansche (5b, 119), die das Gehäuse (2) seitlich verschließen; und
    • einen dritten Flansch (5a), der in dem Gehäuse (2) axialtranslatorisch frei angebracht ist und zwischen den Kolben und einem der Endflansche eine Einlassvorkammer (125) oder eine Auslassnachkammer von Fluiden bildet.
  11. Volumetrische Drehkolbenmaschine nach Anspruch 1, umfassend versenkbare Volumen, die lokal in dem Gehäuse oder der Kurbelwelle eingerichtet sind, die konfiguriert sind, um das Volumen einer von den Kolben definierten Kammer mit veränderlichem Volumen zu vergrößern.
  12. Volumetrische Drehkolbenmaschine nach Anspruch 11, wobei die versenkbaren Volumen Hohlräume (20) einschließen, in denen vorgespannte Kolben (18, 19) gleiten.
  13. Volumetrische Drehkolbenmaschine nach Anspruch 12, wobei die versenkbaren Volumen Hohlräume (20) einschließen, die in Bezug auf die Kammern mit veränderlichem Volumen durch eine flexible Membran (25) abgedichtet sind.
  14. Volumetrische Drehkolbenmaschine nach Anspruch 13, wobei die Hohlräume (20) ein Fluid enthalten, dessen Druck in Abhängigkeit von dem Druck in den Kammern mit veränderlichem Volumen geregelt wird.
EP14719756.0A 2013-04-25 2014-04-25 Volumetrische drehkolbenmaschine mit drei kolben Active EP2989294B1 (de)

Applications Claiming Priority (2)

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FR1353776A FR3005106B1 (fr) 2013-04-25 2013-04-25 Machine volumique rotative a trois pistons
PCT/EP2014/058519 WO2014174103A1 (fr) 2013-04-25 2014-04-25 Machine volumique rotative a trois pistons

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Publication number Priority date Publication date Assignee Title
IT201600123578A1 (it) * 2016-12-06 2018-06-06 Ruggero Libralato Motore a vapore, con statore e pistone a doppio centro di rotazione
IT202100007868A1 (it) * 2021-03-30 2022-09-30 Litm Libralato Innovation Thermal Machines S R L Motore a vapore perfezionato con pistone a doppio centro di rotazione

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US3563680A (en) * 1968-01-08 1971-02-16 Karlheinz Bernhard Kindermann Rotary piston apparatus
DE2047732A1 (de) * 1970-09-29 1972-03-30 Finsterholzl, Georg, 8300 Landshut Umlaufkolbenmotor

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US3160147A (en) * 1964-12-08 hanson
ES256112A1 (es) 1960-02-27 1960-06-01 Martin Artajo Jose Ignacio Sistema mecanico de rotor deformable con embolos rotativos y camara rigida
AT240108B (de) * 1962-11-22 1965-05-10 Johann Ing Geiger Drehkolbenbrennkraftmaschine
US3295505A (en) 1963-05-31 1967-01-03 Jordan Alfred Rotary piston apparatus
FR1404453A (fr) * 1964-02-24 1965-07-02 Mécanisme comportant un rotor articulé
DE1451741A1 (de) * 1964-08-14 1969-02-13 Georg Finsterhoelzl Rotationskolben-Brennkraftmaschine mit eingebautem Vorverdichter
FR1404353A (fr) 1964-08-19 1965-06-25 Barmag Barmer Maschf Dispositif d'alimentation du fil pour machines textiles
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DE2336292A1 (de) * 1973-07-17 1975-02-06 Erich Gustav Glitza Quadrat-rhombus-verbrennungskraftmaschine
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IT1180993B (it) 1984-06-22 1987-09-23 Italo Contiero Macchina volumetrica rotativa
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FR2936272B1 (fr) 2008-09-22 2012-07-13 Vincent Genissieux Machine rotative a losange deformable multifonctions
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US3563680A (en) * 1968-01-08 1971-02-16 Karlheinz Bernhard Kindermann Rotary piston apparatus
DE2047732A1 (de) * 1970-09-29 1972-03-30 Finsterholzl, Georg, 8300 Landshut Umlaufkolbenmotor

Also Published As

Publication number Publication date
FR3005106A1 (fr) 2014-10-31
US20160076373A1 (en) 2016-03-17
EP2989294A1 (de) 2016-03-02
FR3005106B1 (fr) 2017-11-24
WO2014174103A1 (fr) 2014-10-30
US10082028B2 (en) 2018-09-25

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