EP2334906B1 - Mehrfunktionsrotationsmaschine mit verformbarem rhombus - Google Patents

Mehrfunktionsrotationsmaschine mit verformbarem rhombus Download PDF

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Publication number
EP2334906B1
EP2334906B1 EP09741330.6A EP09741330A EP2334906B1 EP 2334906 B1 EP2334906 B1 EP 2334906B1 EP 09741330 A EP09741330 A EP 09741330A EP 2334906 B1 EP2334906 B1 EP 2334906B1
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EP
European Patent Office
Prior art keywords
cavities
machine
cavity
fluid
extrados
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EP09741330.6A
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English (en)
French (fr)
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EP2334906A1 (de
Inventor
Vincent Genissieux
Jean-Thomas Collomb
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GENISSIEUX, VINCENT
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Individual
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Priority to EP16151876.6A priority Critical patent/EP3045656B1/de
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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
    • 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
    • F01C11/00—Combinations of two or more machines or engines, each being of rotary-piston or oscillating-piston type
    • F01C11/002—Combinations of two or more machines or engines, each being of rotary-piston or oscillating-piston type of similar working principle
    • F01C11/004—Combinations of two or more machines or engines, each being of rotary-piston or oscillating-piston type of similar working principle and of complementary function, e.g. internal combustion engine with supercharger

Definitions

  • the present invention relates to a rotary machine with deformable rhombus.
  • a machine generally comprises a stationary assembly or stator and a movable assembly or rotor having a diamond shape articulated at its vertices and rotating around its center, able to deform during its rotation.
  • Each side of the diamond determines with the internal profile of the stator having a generally oval shape, a chamber of variable volume during the movement of the rotor.
  • the sides of the articulated diamond are materialized by plates called pistons having, for the most part, an outer surface of curvilinear shape. These pistons are sometimes provided, in their area of contact with the internal profile of the stator of sealing segments.
  • Such a machine can be used as a combustion engine, turbine, compressor, pump, fan, etc.
  • MRLD Deformable diamond rotating machines
  • a stator generally consisting of a cylindrical non-circular enclosure (a cylinder whose non-circular direction is a cylinder) outside the diamond-shaped rotor and a plurality (the most often four) of rotating elements articulated with each other at their adjacent edges in a pivot connection of an axis parallel to the longitudinal axis of the chamber, each of the rotary elements delimiting with the inner wall of the chamber a chamber or cavity with variable volume.
  • MRLD type explosion engines are described for example in the documents EP 1 295 012 B1 (Nivesh SA ), and US 3,387,596 (L. Niemand ). It was recognized early on that MRLDs can also be used as pumps. This is described for example in patents US 3,295,505 (A. Jordan ) and EP 1 092 838 A2 (J. Sanchez Talero ) and in patent applications WO 86/00370 (I. Contiero ) and WO 2005/106204 (Okulov, P. ).
  • the document WO 86/00370 describes a concept of MRLD comprising four external chambers with variable volume, defined between the outer surface of the rotor, the inner surface of the stator, and an internal chamber of variable volume defined inside the deformable rotor, these chambers being defined axially by two lateral closing flanges.
  • the same fluid is conveyed between the internal chamber functioning as a compressor and the external chambers operating as a motor.
  • a MRLD has several more or less independent cavities, which can be used in different ways.
  • the patent application FR 2 911 631 (Ph.
  • Kuzdzal discloses an internal combustion engine or pressurized gas injection engine having, in addition to external cavities limited by the inner wall of the enclosure and the articulated rotary members, four internal cavities each delimited by the inner walls of adjacent rotating elements and the outer ones of a central tree.
  • the engine comprises two other internal cavities each located at a joint between two movable elements for lubricating the segments of the joint.
  • the lubricating oil can also be used to cool the engine and, in this case, the internal cavities communicate with each other by being connected by oil circulation channels.
  • the oil is fed into an internal lubrication / cooling circuit of the engine by a pump, the internal cavities being used only to open and close valves of the internal circuit of the engine for cooling the engine in a closed circuit. It should be noted that the variation in volume of the internal cavities during a complete cycle of the machine is small, but probably sufficient for a closed circuit operation of the lubricant.
  • the problem that the present invention aims to solve is to present a device compact and simple, comprising a minimum of moving parts, which allows to perform at the same time different fluid processing functions.
  • Another object of the invention is to propose a rotary deformable diamond machine capable of exchanging one or more fluids with one or more external circuits or internal to the machine, so as to vary the dynamic parameters and / or pressure of at least one fluid, simply and reliably over time.
  • Another object of the invention is to provide a deformable diamond rotating machine capable of exchanging one or more fluids with one or more external circuits or internal to the machine, so as to vary the dynamic parameters and / or pressure of at least one fluid, autonomously, without drive by mechanical actuation system of its components.
  • Another object of the invention is to provide a deformable diamond rotary machine having a higher power density and / or function density than known MRLD machines.
  • a rotary deformable diamond machine comprising an enclosure forming a stator adapted to receive a rotor which is a deformable rhombus which is, directly or indirectly (via a seal or the outer surface of a pivoting joint) in contact, with or without clearance, sliding or rolling, with the inner surface of the enclosure, said deformable rhombus comprising a plurality of connected pistons, and preferably four pistons connected, one after the other, by a pivoting joint axis parallel to the longitudinal axis of the enclosure and thus forming a closed chain; the internal surface of the enclosure of said machine defining at least one so-called external cavity, with the extrados of at least one of said pistons, and with the lateral closing walls of the enclosure, and at least one so-called internal cavity being formed inside the rotor with the closing side walls of the enclosure; at least one of the external cavities and / or at least one of the internal cavities being connected, directly or indirectly (for example by means of valve
  • the machine of the invention is therefore able to provide at least three functions, different or identical, in parallel, or in series, or at least one in parallel with two others in series, within at least three cavities with variable volume. distributed in cavities internal to the diamond, or in external cavities and internal to the diamond, in particular by means of exchange zones, said functions being each chosen from: combustion engine, turbine, compressor, pump, metering device, mixer, distributor, flow rate, energy converter, mill, so as to modify at least one of the parameters of the fluid leaving the machine, with respect to the incoming fluid.
  • the machine is able to exchange at least one fluid with an external circuit by at least one of the external cavities and / or by at least one of the internal cavities.
  • external circuit By external circuit, one understands a different circuit of a closed circuit belonging or internal to the machine, such as a closed circuit of lubrication or cooling of the elements of the machine itself.
  • a variable volume cavity is a space defined by the components of the machine, a space whose volume varies during the relative movement of the rotor relative to the stator.
  • This can be achieved with a deformation of the diamond when it rotates inside the fixed chamber of the stator.
  • the objects of the invention are also achieved when the rotor and stator functions are reversed, or when the stator is a non-circular cylindrical profile internal to the diamond.
  • variable volume cavity comprises a cavity associated with a fluid circuit having a function distinct from that of other cavities.
  • a variable volume cavity can be used on a fluid circuit independent of that of the other cavities (for example, with four external cavities and four independent fluid circuits with respect to each other, four separate functions of the machine can be obtained).
  • a variable volume cavity may be associated with a step of transforming one or more fluid parameters belonging to a fluid circuit successively passing through several cavities.
  • variable volume cavities of the machine More precisely, when a fluid circuit passes through the variable volume cavities of the machine in several stages, a cavity of variable volume (or sometimes two or more cavities can be linked when they simultaneously perform the same function (it understands identity of the parameters of the fluid treated by the cavity)) is then associated with a step of transformation of the parameters of the fluid passing therethrough.
  • a plurality of cavities having variable volume geometries are formed within the same machine, between the stator and the rotor, as well as inside the rotor, so that at least three of these cavities can operate simultaneously (where at the same time it is understood that the functions are performed in parallel), or successively (where successively it is understood that the functions are performed in series) as combustion engine, fluid expansion turbine, fluid compressor , pump, metering device, mixer, flow divider, energy converter, mill and this, either independently or by being connected by a fluid exchange.
  • the value of at least one parameter of the fluid that enters the machine is different from that of the same parameter of the fluid leaving the machine, being transformed during the passage of the fluid through one or more cavities of variable volume. the machine, several passages through cavities of the machine that can lead to several changes in the values of one or more parameters of the fluid.
  • parameter of the fluid compressible or not
  • any physico-chemical parameter, quantifiable and measurable, of a nature to characterize this fluid and / or its state such as for example: pressure, temperature, velocity, vorticity, the chemical composition (case of fuels, lye %), the viscosity, the shear rate (case of pasta), the granulometry (case of crushing), the homogeneity (case of mixing, mixing in centrifugation ), concentration ...
  • a rotary deformable diamond machine makes it possible to provide a higher power density than known MRLD machines.
  • power density is meant the useful power of the machine per unit volume of the space occupied by this machine.
  • the exploitation of several successively variable volume cavities (in series) within one and the same machine makes it possible, overall, to perform a function for treating the same fluid in several sub-functions of the same nature and operating on ranges. different from at least one of the parameters of this fluid.
  • the machine of the invention can thus fulfill at least three different functions simultaneously, or in parallel, of which at least one can be a motor function, within 3 distinct variable volume cavities.
  • Three or more devices are thus obtained using the thermodynamic parameters of one or more fluids which are integrated into a single machine, judiciously exploiting the variable geometry volumes created inside the machine during the deformation of the resulting diamond.
  • a relative movement between the rotor and the stator of the machine (more particularly, the pistons of the rotor have a rotational movement about the longitudinal axis of the enclosure and a rotational movement around the center of the sides of the diamond) .
  • the variations in speed and / or pressure and / or temperature of a fluid admitted into the machine may cause the diamond to rotate, or conversely, the rotation of the diamond can cause variations in speed and / or pressure and / or temperature of a fluid admitted into the machine, before its delivery, the rotation of the diamond which, by the variation of the volume of the cavities, internal or external thus created, varies the pressure and / or the temperature of a treatment fluid.
  • This variation would then be done in several steps, for example to obtain several pressure stages of the same fluid, or even to use a first pressure of a fluid to trigger a pressure change of another fluid.
  • the machine of the invention can also fulfill at least three identical functions successively, or in series, within at least 3 cavities with different variable volume.
  • the engine of the invention can fulfill at least three functions within three cavities with different variable volume, two of these functions being identical and successively fulfilled (in series) while the third function is different from the first two and is filled simultaneously (in parallel).
  • the object of the invention is also achieved with a machine operating as a multipump and / or multiturbine and / or multicomputer.
  • the diamond can be driven by a fluid (the machine then comprises at least one turbine and at least two pumps operating in series and / or in parallel, or at least two turbines operating in series and / or in parallel associated with at least a pump) or by a motorized drive shaft, all these devices of the multipump or multiturbine type being integrated into the mechanics of the same machine.
  • such a multifunctional deformable rhomboid rotary machine makes it possible to use different fluids (air, water, oil, etc.) and to integrate several functions of transformation of one or more several thermodynamic parameters of the fluid or fluids used, or even conversion of the energy of this fluid (s), for a simplified mechanical structure and for a small size, compared to known machines performing the same functions.
  • Multipump or multiturbine operation or multi-compressor of such a machine advantageously finds its application in the case of complex hydraulic or pneumatic circuits that require regulation.
  • Such a machine can be used as a power adapter, for example by using, at the inlet, a high-flow, low-pressure fluid to obtain at the outlet a fluid having a small flow rate and a higher pressure. It is also possible to obtain a three-stage compressor with the same machine. Such a machine also finds its application when one wants to achieve a coupling of a hydraulic circuit with a pneumatic circuit using different fluids. We can thus, for example, driving a water pump with a hydraulic motor and cooling the entire machine with compressed air, all in one machine.
  • the machine comprises means for transferring or exchanging fluid from one variable volume cavity to another.
  • These transfer or exchange means are in particular orifices or channels formed in the pistons, the pivots, the side flanges, the profile of the enclosure or the transmission device.
  • the external cavities are peripheral extrados cavities, each being defined between the extrados face of a piston, the inner surface of the enclosure and the lateral closure flanges.
  • the external cavities are extrados circular cavities, each being defined by the extrados faces of two adjacent pistons, the pivoting joint connecting them, the inner surface of the enclosure and the lateral closure flanges. .
  • the device of the invention makes it possible to use up to four external cavities with the same fluid or with different fluids.
  • an internal cavity is any cavity included within the rhombus.
  • Such an internal cavity has at least one surface in common with the intrados face of at least one of the pistons or with the underside of at least one of the pivoting joints or with at least one intermediate piece connected to the one of the pistons or one of the pivoting joints.
  • the internal cavities whose volume is caused to vary with the rotation of the rotor relative to the stator of the machine, are chosen from: the peripheral intrados cavities, the intrados circular cavities, the central cavities, the central cavities divided by one or two diagonals, the central cavities divided by one or two medians, the cylindrical cavities, the eccentric or centered toric cavities, the helical cavities, or a combination of several such internal cavities.
  • said internal cavity is a circular intrados cavity formed by the space between the intrados faces of two associated pistons, a cylinder of internal revolution to the deformable rhombus and the lateral closure flanges.
  • said internal cavity is an external eccentric toroidal cavity defined by the space between the outer surface of a sliding toric device whose ends bear on two associated pistons, the intrados faces of the two associated pistons, the pivoting joint. and the lateral closing flanges.
  • said internal cavity is an internal eccentric toric cavity defined by the space between the piston of a first toric device and the cylinder of a second complementary O-ring device, the piston bearing on one of the pistons and the cylinder on another piston adjacent to the first, and the lateral flanges of closure.
  • said internal cavity is an eccentric central cavity defined by the space between the central axis of the rhombus, the outer surface of a toric device whose ends rest on two median arms of the rhombus and the lateral closure flanges. .
  • At least two of said outer peripheral cavities, or at least two of said internal cavities, or at least two of the outer and inner cavities carry a different fluid.
  • the machine comprises fluid exchange zones with the external cavities, these zones being channels formed in the pistons, the pivots, the flanges, the profile of the enclosure or the transmission device.
  • the machine of the invention uses the same working fluid which is transferred, during its operation, between one of the outer cavities and one of the internal cavities.
  • the machine comprises fluid exchange zones with the intrados cavities, these zones being channels formed in the pistons, the pivots, the flanges, the central shaft of the machine or the transmission device.
  • the pistons, the inner surface of the enclosure, the arms of the diagonals or the median arms are provided with fins so that the variations of the dynamic parameters of the fluid predominate over the variations of the static parameters.
  • the machine to combine the dynamic effects, due to the speed of the fluid or fluids it conveys, and the static effects due to the pressure of the fluid or fluids carried by the machine.
  • the variation of the dynamic parameters of the fluid is greater than the variation of the static parameters of the same fluid. This also allows the machine to promote heat exchange through dynamic effects and the largest heat exchange surface.
  • the machine of the invention can be reversible.
  • this offers the advantage of being able to integrate the machine into energy recovery processes, in particular in a storage dam where the machine can operate as a turbine to produce electrical energy or as a pump for absorbing the energy of the machine.
  • network :
  • a machine comprising at least one internal cavity and at least one external cavity, or comprising at least two different internal cavities, within which the same fluid passes through, will benefit from a facility of performing dynamic sealing between said cavities through an intermediate pressure bearing effect.
  • a machine comprising at least two cavities of variable volumes, internal and / or external, which successively provide at least two treatment functions of the same nature on the same fluid, may have a better isentropic efficiency by the addition of a heat exchanger (external to the machine or built into the machine housing) between the two cavities.
  • a heat exchanger external to the machine or built into the machine housing
  • exchange channels of a third heat transfer fluid can be made in the components of the machine, so as to transmit the calories generated in the cavities with variable volume of the second function to the variable volume cavities of the first function, and thus improve the overall isentropic efficiency of said machine.
  • the objects of the invention are also achieved with a pump, a turbine, a motor or a compressor having the features of a machine of the invention.
  • the invention relates to a rotary deformable diamond machine (MRLD) comprising a stator 2 having a generally tubular shape of approximately oval section, whose profile is in accordance with the geometric rules imposed by the deformation of the diamond during its rotation and of which the inner surface defines an enclosure 1 for receiving a rotor 3 which is a deformable rhombus 4.
  • the deformable rhombus 4 is a set of four pistons 6 interconnected by pivot links, materialized by pivoting joints 7, and which form a chain closed on itself.
  • the rotor 3 is generally the rotating part of the machine, but it is possible, in a variant, to drive the chamber 1 in rotation which then rotates relative to the rhombus 4 fixed in rotation but whose sides are deformed (the side segment that connects, in a plane perpendicular to the axis of rotation of the machine, the axes of two adjacent pivot links).
  • the projections of the axes of pivotal connections of the pistons in a plane perpendicular to the axis of rotation of the machine represent the vertices 5 of the diamond.
  • the segment that connects two opposing vertices 5 forms a diagonal of the rhombus. It will be understood in the following, also diagonally a part or mechanical connection built according to this segment.
  • a piston 6 is a part having a shape of cylinder portion of director parallel to the axis of rotation of the machine.
  • the surfaces located at the two ends of this piece each provide a part of a rotational axis pivot connection parallel to the axis of rotation of the machine.
  • the segment that connects two midpoints of opposite sides of the rhombus, including two opposed pistons, forms a median of the rhombus.
  • median also a part or mechanical connection built according to this segment. The intersection of the diagonals or medians of the diamond defines the center of the machine.
  • rotation shaft 57 ( fig.23 ) or central shaft of the machine, it comprises a part or a set of mechanical parts for recovering the rotational movement of the rotor or the stator via a suitable mechanical transmission system.
  • the machine also comprises two lateral flanges 12, 13 of closure ( fig.20a ), arranged perpendicularly to the rotation shaft of the machine and bearing against the front and rear faces of the stator and the rotor.
  • the extrados 9 of the piston comprises the outer surface of the piston 6, located outside the rhombus 4, and the lower surface 11 of the piston, the inner surface of the piston 6, located at the inside the diamond 4.
  • volume of the machine it comprises the revolution cylinder closed by the side flanges and encompassing the outer profile of the stator of the machine according to a conventional embodiment or encompassing the most eccentric piece relative to the axis of rotation.
  • the invention uses the property of the deformable diamond rotary machine provided with means of the invention to create cavities whose volume varies during the deformation of the rhombus, these external cavities and internal to the rotor (or rhombus) can be realized in different ways.
  • an external cavity 8 (external to the rotor 3) is formed by an extrados peripheral cavity 14.
  • Such an extrados peripheral cavity 14 is formed by the extrados face 9 of one of the pistons 6 of the diamond 4 against the inner wall of the stator 2 and the closing flanges 12, 13 on either side of the machine.
  • the figure 1 shows the example of the extrados peripheral cavity 14 left. In the initial position ( figure 1a ), the peripheral cavity extrados in the lower part is initially empty, or at minimum volume.
  • the following figures (1b to 1f) show the evolution of this cavity (represented as a dotted line) when the diamond 4 rotates in the direction indicated on the Fig.
  • the figure does not represent the filling devices.
  • the figure 1b shows the beginning of the admission.
  • the figure 1c shows a state of the admission phase where the cavity increases in volume.
  • the left extrados peripheral cavity 14 has reached its maximum volume; preferably, the diamond 4 then takes the form of a square.
  • the volume of the cavity decreases and the fluid is evacuated.
  • the delivery devices are not shown in this figure.
  • the left extrados peripheral cavity 14 reaches its minimum volume or empties completely.
  • each extrados 14 peripheral peripheral cavity performs a cycle by half-turn.
  • the displacement of such a cavity represents approximately 1/50 th of the machine volume, ie a displacement of 4/50 th of the machine volume per revolution.
  • these extrados peripheral cavities 14 can be accessed by channels made in the pistons 6, or in the pivots 7 or in the stator 2 or in the lateral flanges 12, 13 as will be explained later.
  • extrados peripheral cavities 14 may have the same function (pump, compressor, motor, etc.) or not.
  • a cavity can receive a pressurized gas that sets the rotor in motion, while the others work as a compressor or as a pump. If several cavities work as a pump, they can work with the same fluid or with a different fluid.
  • the extrados peripheral cavities 14 using the same inner wall of the stator there is a risk of contamination between the different fluids extrados peripheral cavities 14, because there will always be a permanent film that is formed on the inner wall.
  • an external cavity is an external junction cavity defined by the space between two pistons 6 connected to the rotor 3 or which have a pivot connection (or pivot joint) 7 in common and the inner wall of the stator 2 (or enclosure 1), four cavities thus being defined in the space between the rotor 3 and the stator 2.
  • the stator 2 may have an enclosure 1 of elliptical or circular shape. In the case where the enclosure is circular, it has a longitudinal axis which is common with that of rotation of the machine and the cavity defined with the lateral closure flanges is an extrados circular cavity 15. Such an extrados circular cavity 15 performs a cycle by half turn of rotation of the rotor, and the four cavities succeed one another.
  • the displacement of the extrados circular cavity 15 may represent 1/100 th of the volume of the machine, ie a displacement of 2/25 th of the machine volume per revolution if the cycles performed at each half-turn and the four cavities are accumulated on the same function.
  • the guide of the deformation of the rotor 3 is formed by a central shaft of elliptical section 16.
  • the volume of this cavity varies according to the position of the rotor 3, in particular, it grows from a position where the volume is minimal ( fig.3a ) at a fluid inlet position ( 3B ), reaches its maximum volume in maximum deformation position of the diamond 4 ( Fig.3c ), to decrease further and compress the fluid ( fig.3d ) before completely removing it from the extrados circular cavity 15 (diamond position similar to that of position 3a).
  • these circular cavities can be accessed extrados 15 by channels made in the pistons 6, or in the pivots 7 or in the stator 2 or in the lateral flanges 12, 13 closing.
  • this variant embodiment comprises a constructive simplification associated with a significant reduction in the manufacturing cost, insofar as the stator 2 and the enclosure 1 can be obtained directly from a standard profile of circular section, avoiding machining operations by removal of material.
  • the machine illustrated in figures 3 has a number of extrados circular cavities of 8 per turn, a number of intrados peripheral cavities 17 of 8 per turn, which makes an instantaneous total number of 8 cavities, which can fulfill four functions.
  • a working cavity is formed by an internal cavity of the rotor 3.
  • This cavity uses a profile internal to the diamond 4, this profile being of the MRLD type. , ie a profile which respects the laws of deformation of the diamond, which is, in a first variant illustrated in Figures 4a to 4d associated with the inner surface called the intrados face 11 of the pistons 6.
  • the figure 4a shows an example of four peripheral intrados cavities 17, two on the left and two on the right, as seen with respect to a vertical axis passing through the center of the rotor 3. It is also possible to use, alternatively or at the same time, the peripheral cavity left intrados or the right one.
  • the extrados cavities 14 left and 17 left intrados are in phase opposition (the volume of one increases, while the volume of the other decreases with the rotation of the diamond 4, and reaches a maximum value while the value the other is minimal) and it is the same for the extrados cavities 14 and intrados 17 right.
  • the cubic capacity of a peripheral intrados cavity 17 is slightly lower than that of the extrados peripheral cavity 14, this difference in displacement is essentially related to the thickness of the pistons.
  • the ratio of the cubic capacity of the intrados cavities to that of the extrados cavities is less than 1.
  • peripheral intrados cavities 17 can be accessed by channels made in the pistons 6, or in the pivots 7 or in the stator 2 or in the lateral flanges 12, 13 of closure.
  • the machine illustrated in figures 4 has two left extrados peripheral cavities 14, two extrados straight peripheral cavities 14, two left intrados peripheral cavities 17 and two right intrados peripheral cavities 17, which makes an instantaneous total number of 8 cavities, which can fulfill four functions.
  • FIGS. 3a to 3d show also peripheral cavities 17, left and right, which can be combined with extrados circular cavities 15, as it has been explained above, to obtain up to eight different working cavities.
  • the internal cavities are intrados circular cavities 18, a cavity being formed by the space between two pistons 6 connected (or having a pivot connection 7 in common), a cylinder of revolution 19 internal to the diamond 4, the longitudinal axis is common to the central shaft of the machine.
  • a circular cavity intrados 18 performs a cycle by half-turn and the four cavities succeed one another.
  • the displacement of such a circular intrados cavity 18 represents approximately 1/100 th of the volume of the machine, ie a displacement of 2/25 th of the volume of the machine per revolution if the four cavities are combined and both cycles per revolution.
  • the deformation of the rhombus 4 is in this case guided by the internal profile of the chamber 1 of the stator 2.
  • these circular cavities can be accessed. 18 by channels in the pistons 6, or in the pivots 7 or in the stator 2 or in the side flanges 12, 13 closing.
  • the machine illustrated in figures 5 has two left extrados peripheral cavities 14, two extrados straight peripheral cavities 14, and four intrados circular cavities 18, which makes an instantaneous total number of 8 cavities, which can fulfill four functions.
  • a working cavity formed by a central internal cavity 20 of the rotor 3 is used.
  • This central internal cavity 20 is between the inner surface called the intrados face 11 of all the pistons 6 and the lateral closure flanges (not shown).
  • the central internal cavity 20 is initially at minimum volume.
  • the following figures (6b to 6d) show the evolution of this cavity (represented as a dotted line) when the rhombus 4 rotates in the direction indicated in the figure. The figure does not represent the filling devices.
  • the figure 6b shows the beginning of the admission, the cavity continues to increase in volume during the entire admission phase.
  • the cavity has reached its maximum volume; preferably, the diamond 4 then takes the form of a square. Then ( figure 6d ), the volume of the cavity decreases and the fluid is evacuated, the cavity then reaches its minimum volume, which corresponds to the end of the discharge and the beginning of the admission for the next cavity.
  • a central internal cavity 20 carries out 4 cycles per revolution, thus a cycle twice as short as that of an extrados peripheral cavity 14.
  • the displacement of this zone represents approximately 1/40 th of the volume of the machine, that is 1/10 th of the volume of the machine per revolution.
  • this central internal cavity 20 can be accessed by a rotation shaft (not represented), by the pivots 7 or by the lateral flanges 12, 13 of closure.
  • a machine that would use in combination the extrados peripheral cavities 14 and this central internal cavity 20 could then have five different working cavities, each able to operate independently.
  • the machine illustrated in Figures 6a to d has a number of left extrados peripheral cavities 14 of 2 or 4 per turn, a number of extrados straight peripheral cavities 14 of 2 per turn, and a central cavity, which makes an instantaneous total number of cavities, which can fulfill three functions.
  • a working cavity is made by a central cavity of the rotor or rhombus 4 divided by a diagonal 21.
  • This cavity is between the inner surface called the intrados face 11 of two pistons 6 connected and the diagonal connecting them .
  • the central cavity of the rotor divided by a diagonal 21 is initially at minimum volume.
  • the following figures (b to d) show the evolution of this cavity (shown hatched) when the diamond 4 rotates in the direction indicated in the figure. The figure does not represent the filling devices.
  • the figure 7b shows the beginning of the admission, the cavity continues to increase in volume during the entire admission phase.
  • the cavity has reached its maximum volume; preferably, the diamond 4 then takes the form of a square.
  • the volume of the cavity decreases and the fluid begins to be evacuated.
  • the cavity reaches its minimum volume, which corresponds to the end of the discharge and the beginning of the admission for the next cavity.
  • Such a central cavity of the rotor divided by a diagonal 21 performs four cycles per revolution and two cavities succeed one turn, thus a cycle two times shorter than that of an extrados peripheral cavity.
  • the cubic capacity of this zone represents approximately 1/80 th of the machine's volume, ie 1/20 th of the machine's volume per revolution.
  • these cavities can be accessed by a rotation shaft (not shown), by the pivots 7, or by the lateral flanges 12, 13 of closure.
  • a diagonal divides the central cavity into two parts, which makes it possible to set up two devices of the same displacement within the machine. These devices can be independent or mechanically linked or can exchange a fluid between them.
  • a machine that would use in combination the outer peripheral cavities 14 and two such central cavities divided by a diagonal 21 could then have six different working cavities, each able to operate independently.
  • the changes in the length of the diagonal of the rotor can be compensated by a slide 22, a membrane or other device to compensate for a variation length of the diagonal wall and at the same time ensure the sealing of the cavity.
  • the cylindrical slide cavity 23 shown hatched on the figure 7f
  • the volume of this cylindrical slide cavity 23 can vary between a minimum volume, the slide then having the length of the small diagonal (as in the position illustrated in Figure 7c ) and a maximum volume shown in figure 7f when the slide 22 reaches the length of the large diagonal.
  • a machine that would use in combination the extrados peripheral cavities 14 and two such central cavities divided by a diagonal 21 and where each diagonal had a cylindrical cavity 23 slide with variable volume could then have seven different working cavities, each able to operate independently.
  • the machine illustrated in figures 7 has two left extrados peripheral cavities 14, two extrados straight peripheral cavities 14, two central cavities divided by a diagonal 21 and a cylindrical slide cavity 23, which makes an instantaneous total number of 7 cavities, which can fulfill five functions.
  • an internal working cavity is formed by a central cavity of the rotor divided by the two diagonals 25 of the diamond 4. This cavity is between the inner surface called the intrados face 11 of a piston 6 and the two diagonals connecting its pivoting joints 7 In the initial position ( figure 8a ), the cavity is initially at minimal volume.
  • the following figures (8b to 8e) show the evolution of this cavity (represented as a dotted line) when the rhombus 4 rotates in the direction indicated in the figures. The figures do not represent the filling devices.
  • the figure 8b shows the beginning of the admission, the cavity continues to increase in volume during the entire admission phase.
  • the cavity has reached its maximum volume; preferably, the diamond 4 then takes the form of a square. Then ( figure 8d ), the volume of the cavity decreases and the fluid begins to be evacuated. In figure 8e the cavity reaches its minimum volume, which corresponds to the end of the discharge and the beginning of the admission for the next cavity.
  • Such a central cavity of the rotor divided by the two diagonals 25 performs four cycles per revolution and four cavities succeed one turn, thus a cycle two times shorter than that of an extrados peripheral cavity.
  • the displacement of this cavity alone and on a single cycle represents approximately 1/160 th of the volume of the machine, ie a cubic capacity of 1/10 th of the volume of the machine per revolution and for the four cavities.
  • these cavities can be accessed by a rotation shaft (not shown), by the pivots 7 or by the lateral flanges 12, 13 of closure.
  • the diagonals divide the central cavity into four parts, which makes it possible to set up four devices of the same displacement within the machine. These devices can be independent (operate independently of one another) or be mechanically linked or can exchange fluid between them. A machine which would use in combination the extrados peripheral cavities 14 and four such central cavities divided by two diagonals 25 could then have eight different working cavities, each able to operate independently.
  • the changes in length of the diagonal rotor can be compensated by a slide, a membrane or other device to compensate for a variation in length of the diagonal wall and at the same time ensure the sealing of the cavity.
  • a central cylindrical cavity 26 can be made at the center of the diagonals of the rhombus 4, the cavity being formed by four sliding pistons 27 ( fig.8c ), being arranged in pairs on the same diagonal and sliding in opposite directions, to vary the volume of a central cylindrical cavity 26.
  • This central cylindrical cavity 26 and its volume variations during the rotation of the rhombus are more visible to the Figures 8a to 8e .
  • the cavity In the initial position ( figure 8a ), the cavity is initially at minimal volume.
  • the following figures (8b to 8e) show the evolution of this cavity 26 (shown hatched) when the diamond rotates in the direction indicated in the figures. The figures do not represent the filling devices.
  • the figure 8b shows the beginning of the admission, the cavity 26 continues to increase in volume during the entire admission phase.
  • the cavity 26 has reached its maximum volume; preferably, the diamond then takes the form of a square.
  • the volume of the cavity 26 decreases and the fluid begins to be evacuated.
  • the cavity 26 reaches its minimum volume, which corresponds to the end of the discharge and the beginning of the admission.
  • this central cylindrical cavity 26 can be accessed by a rotation shaft (not shown), by the pivots 7 and the sliding pistons 27, or by the lateral flanges 12, 13 closing.
  • a machine which would use in combination the extrados peripheral cavities 14, four central cavities divided by two diagonals 25 and a central cylindrical cavity 26 with variable volume could then have nine different working cavities, each able to operate independently.
  • the machine illustrated in figures 8 has two left extrados peripheral cavities 14, two extrados straight peripheral cavities 14, four central cavities divided by the two diagonals 25 and a central cavity 26, which makes an instantaneous total number of 9 cavities, which can fulfill seven functions.
  • a working cavity is made by a central cavity of the rotor divided by a median 28 of the diamond 4. This cavity is between the inner surface called the intrados face 11 of a piston 6 and the median 30 connecting the centers of the two pistons 6 opposed.
  • the cavity In the initial position ( figure 9a ), the cavity is initially at minimal volume.
  • the following figures (9b to 9c) show the evolution of this cavity (filled with dots) when the diamond rotates in the direction indicated in the figures. The figures do not represent the filling devices.
  • the figure 9b shows the position in which the cavity has reached its maximum volume; preferably, the diamond then takes the form of a square. Then, the volume of the cavity decreases and the fluid begins to be evacuated.
  • the cavity reaches its minimum volume, which corresponds to the end of the discharge and the beginning of the admission for the next cavity.
  • a central cavity of the rotor divided by a median 28 performs four cycles per revolution and two cavities succeed one turn, thus a cycle twice as short as that of an extrados peripheral cavity.
  • the cubic capacity of this zone represents approximately 1/80 th of the volume of the machine, ie a cubic capacity of 1/10 th of the machine volume per revolution.
  • these cavities can be accessed by a rotation shaft (not shown), by the pivots 7 or by the lateral flanges 12, 13 of closure.
  • FIG. 9 This embodiment has the advantage of a constructive simplification, the median does not change length during the rotation and, therefore, simplified seals can be used.
  • the machine illustrated in figures 9 has two left extrados peripheral cavities 14, two extrados straight peripheral cavities 14, two central cavities divided by a median 28, which makes an instantaneous total number of 6 cavities, which can fulfill four functions.
  • a working cavity is made by a central cavity of the rotor divided by two medians 29 of the diamond 4. This cavity is between the inner surface called the intrados 11 of two pistons 6 connected, their pivoting joint 7 and the two adjacent segments each corresponding to half of each of the two medians 30 connecting the midpoints of opposed pistons 6.
  • the cavity In the initial position ( figure 10a ), the cavity is initially at minimal volume.
  • the following figures (10b to 10c) show the evolution of this cavity (shown dashed) when the diamond rotates in the direction indicated in the figures. The figures do not represent the filling devices.
  • the figure 10c shows the position where the cavity has reached its maximum volume; preferably, the diamond then takes the form of a square. Then, the volume of the cavity decreases and the fluid begins to be evacuated. In figure 10c , the cavity reaches its minimum volume, which corresponds to the end of the discharge and at the beginning of admission for the next cavity.
  • Such a cavity performs four cycles per revolution and four cavities succeed each other on one revolution, thus a cycle twice as short as that of an extrados peripheral cavity.
  • this central cavity of the rotor divided by two medians 29 represents about 1/160 th of the volume of the machine, that is to say a cubic capacity of 1/10 th of the volume of the machine per revolution.
  • these cavities can be accessed by a rotation shaft (not shown), by the pivots 7 or by the lateral flanges 12, 13 of closure.
  • this embodiment has the advantage of a constructive simplification, because the medians of the diamond do not change length during the rotation thereof.
  • the machine illustrated in figures 10 has two left extrados peripheral cavities 14, two straight extrados peripheral cavities 14, four central cavities divided by the two medians 29, which makes an instantaneous total number of 8 cavities, which can fulfill six functions.
  • a working cavity is formed by an eccentric toroid cavity located inside the rotor 3, two eccentric toroidal cavities 31, 32 being illustrated in FIGS. Figures 11a to 11c .
  • One of these cavities, called external eccentric toroidal cavity 31 is formed by two toroidal devices of complementary section (for example of the piston type sliding in a cylinder), which can move in an arc following the deformation of the rhombus, taking each bearing on a piston 6 and closing a volume defined by a pivoting joint 7 of the diamond 4, the intrados face 11 of two pistons 6 connected connected by the pivoting joint 7 and the outer surface of the toric devices 33.
  • a second internal toric cavity 32 is formed inside one of the toric devices 33 (for example of the cylinder) during the displacement, relative to the first, of a second cylindrical device (the piston).
  • the cavity In the initial position ( figure 11 (b) , the cavity is at minimal volume.
  • the cavity On the figure 11c , the cavity has reached its maximum volume, then the volume of the cavity decreases and the fluid begins to be evacuated.
  • these cavities can be accessed by a rotation shaft (not shown), by the pivots 7 or by the lateral flanges 12, 13 of closure.
  • toric cavities can thus be made inside the rotor, for example by arranging them around each pivoting articulation of the diamond.
  • a machine that would use in combination four external cavities, four outer eccentric toroidal cavities, and four internal toric cavities and a central cavity with variable volume could then have thirteen different working cavities, each of which can operate independently.
  • the central cavity may itself be subdivided into several cavities by a membrane wall as described in the embodiment illustrated by FIG. figure 14 , which increases the total number of cavities with variable volume.
  • the machine illustrated in figures 11 has two left extrados peripheral cavities 14, two extrados straight peripheral cavities 14, one to four external eccentric toroidal cavity 31, one to four internal toroidal cavities 32 and a central cavity 20, which makes an instantaneous total of 13 cavities, which can fill eleven functions.
  • Variable volume toric cavities can be made in the center of the deformable diamond rotor. Such a cavity is made around the central axis passing through the point of intersection of the medians 30 and is delimited by two toric devices sliding in an arc of a circle, each bearing on a median arm 30. In the initial position, represented at figure 12b the central toric cavity 34 is at a minimum volume. The volume of the cavity increases with the rotation of the rotor and reaches its maximum volume ( Fig. 12c ), then the volume of the cavity decreases and the fluid begins to be evacuated. As in the example of Figures 11a to 11c very small volume toric cavities may also be formed inside the toric devices.
  • these cavities can be accessed by a rotation shaft (not shown), by the pivots 7 or by the lateral flanges 12, 13 of closure.
  • These cavities internal to the rotor can be used in addition to the external cavities of the machine, as described in the first embodiment, and a machine is thus obtained that can perform several functions (motor, energy transformation, pumping). , compression) simultaneously (in parallel) or successively (in series).
  • the machine illustrated in figures 12 has two left extrados peripheral cavities 14, two straight extrados peripheral cavities 14, one to four central toric cavities 34, one to four outer eccentric toric cavities 31, which makes an instantaneous total number of 12 cavities, which can fulfill ten functions.
  • Compressed air fills the cavities 14.
  • the air pressure drives the rotor in rotation.
  • the air emerges from the cavities 14 of the machine at a pressure lower than that of the inlet.
  • the cavities 14 fan the air.
  • Pasta is dosed into the cavities 29 before being transferred to the central toric cavities 34 (only one cavity 34 is shown in the figures for the sake of simplification, but it is nevertheless possible to envisage the use of four central toric cavities 34 34 with the illustrated machine).
  • the pasta thus dosed by the first cavities 29 is admitted into the cavities 34.
  • the rotation of the rotor causes the volume of the cavity 34 to decrease, which allows mixing and injection of this paste into the discharge circuit of the machine. .
  • the design of the machine is facilitated by adapting the cubic capacities of the cavities to the needs of the plant automat.
  • the cavities may have a dead volume of about zero to avoid dead zones harmful to food safety.
  • the construction allows a very easy cleaning of the machine.
  • the turbining and compression are simultaneous (parallel operation) while the dosing and injection of the pasta are done successively (for series operation).
  • the machine may include external cavities, as described in the first embodiment, and a helical internal cavity.
  • the helical internal cavity can be made between a solid screw moving in an adjusted blind tapping.
  • the tapping can be rotated by one of the middle arms of the rotor, the screw being fixed or rotated by the other median arm.
  • the speed difference between the tapping and the screw causes a change in volume of the helical internal cavity.
  • the displacement of the helical internal cavity is very small, the pressure generated can then reach very high values.
  • FIGS. 13a and 13b illustrate an exemplary embodiment of a machine according to the invention comprising four extrados peripheral cavities 14 and a central internal cavity 20.
  • the central internal cavity 20 is delimited by the space between the internal surfaces or intrados faces 11 of the four pistons 6 and four flexible membranes 35 attached to the pistons 6 at their pivoting joints 7.
  • the flexible membrane 35 has two end tongues 36,37 connected by a bellows 38.
  • the tongues 36,37 serve as fixing means for the pistons 6, one of the end tabs 36 bearing on the inner surface of a piston 6, the bellows 38 coming from covering the pivoting joint 7 and the other end tongue 37 bearing on the piston 6 connected to or adjacent to the previous one.
  • the bellows 38 deforms and seals in the central internal cavity 20 as well as the sealing of the extrados peripheral cavities 14 through the pivoting joint 7.
  • Inlet / outlet in the external cavities allow access of a fluid in the external cavities of the machine, this fluid being able to communicate with the internal cavity through orifices made through the pistons 6 of the rotor 3.
  • the figure 14 illustrates another embodiment of a machine according to the invention wherein the pivoting joints 7 of the rhombus 4 are protected by flexible membranes 35 of the type previously described, but where the central cavity 20 comprises a flexible membrane wall 39 arranged according to the one of the diagonals of the rhombus 4, so as to connect two pivoting joints 7 opposite.
  • This membrane wall 39 then divides the internal central cavity into two central cavities of the rotor divided by a diagonal 21, having the same volume.
  • the arrows of the figure 14 illustrate the circuit of a treatment fluid inside the machine from its input (arrow E) to its exit (arrow S).
  • the machine illustrated in figure 14 receives as input a fluid to be treated in the axial direction (arrow E), this fluid undergoing a first thermodynamic operation (in particular compression or expansion) within the first central cavity divided by a diagonal 21 of the machine.
  • the fluid is then sent into the extrados peripheral cavities 14 via valve orifices 40 closing the channels formed in the pistons 6.
  • the fluid undergoes another operation in the extrados peripheral cavities 14 and is then pushed back into the second central cavity.
  • the fluid undergoes a third operation in the second central cavity divided by a diagonal 21, and is then pushed out of the machine in an axial direction of exit (arrow S).
  • the machine illustrated in figure 14 has two left extrados peripheral cavities 14, two extrados straight peripheral cavities 14, two central cavities divided by a diagonal 21, which makes an instantaneous total number of 6 cavities, which can fulfill three functions.
  • the machine is designed to generate a dynamic pressure which is added to the static pressure due to the deformation of the receiving cavity of the working fluid that it sets in motion.
  • This dynamic pressure is obtained by providing fins with the stator 2, the rotor 3, the arms of medians 30 or the arms of the diagonals 41,42.
  • Figures 15a and 15b illustrate an embodiment where the pistons 6 are provided with fins 44 on the lower surface and fins 43 on the upper surface, these fins being inclined and uniformly distributed on the lower surface and on the upper surface of the pistons.
  • a rotor 3 provided with vanes 43,44 rotating inside a stator 2 with a smooth inner surface allows the machine to have a centrifugal pump or turbine operation if the chamber is the stator. If the enclosure rotates while the diamond is fixed in rotation, the fins of the pistons 6 will behave as a rectifier.
  • FIGS. 16a and 16b illustrate another embodiment where the inner surface of the chamber 1 of the stator 2 is provided with fins 45 which are inclined and uniformly distributed on the inner surface of the stator.
  • the spacing of the fins may be variable.
  • a rotor 3 having a smooth extrados face 9 rotating inside a stator 2 provided with fins 45 then allows the machine to operate as a hydraulic or pneumatic rectifier if the enclosure is the stator. If the chamber rotates while the diamond is fixed in rotation, the fins of the chamber 1 will behave as a centrifugal pump or turbine.
  • each median arm 30 is provided with fins 46 with inclined walls thus forming a propeller 47 with four blades (or more) inside the rotor 3.
  • This solution is particularly advantageous because very simple the length of the median arms 30 being constant. Furthermore, the flow of fluid inside the rotor was less turbulent than when passing inside a rotor with fins on the underside of the pistons.
  • FIGS 18a and 18b illustrate yet another embodiment where the arms of the diagonals 41,42 are provided with fins 48 with inclined walls thus forming a propeller 49 with four blades (or more) inside the rotor or the diamond 4.
  • the advantage of such an arrangement of fins is that the rotational speed of the diagonal arms being constant, the flow of the fluid is less turbulent than when passing inside a rotor provided with fins on the underside pistons.
  • the blades 48 of the propeller 49 are telescopic in order to be able to adapt to the length variation of the arms of the diagonals 41, 42 during the rotation of the diamond 4.
  • Each blade 48 of the propeller comprises, in the direction of a 41,42 diagonal arm, a fixed portion 50 bearing on the periphery of a pivoting joint 7 which is slidable, during the rotation of the diamond 4, inside a wing portion 48 belonging to a central hub of propeller 49.
  • both the stator 2 and the rotor 3 may be provided with fins of the type 43,44 for the pistons 6 of the rotor 3 or 45 for the stator 2. It is also possible to envisage use a finned stator capable of receiving a rotor provided with fins 46 on the arms of its medians or a rotor provided with fins 48 on the arms of its diagonals.
  • the extrados fins 43, the intrados fins 44, the stator fins 45, the median arm fins 46, the propellers 47,49, the diagonal arm fin 48 and the fixed wing portion 50 promote heat exchange.
  • the rotary deformable diamond machine of the invention makes it possible, by virtue of its construction with at least three variable volume cavities, to perform several functions chosen from those of: motor, pump, compressor or turbine, or a combination thereof a fluid exchange being established with one or more external circuits to the machine, as well as between the various variable volume cavities thereof.
  • the exchange zones (or means of transfer or exchange) of fluid within the machine are illustrated in the Figures 19 to 23 . These exchange zones are inlet or discharge ports communicating, on the one hand, with fluid circuits external to the machine and, on the other hand, with channels formed within its elements opening into external cavities. or internal of the machine, as will be explained later.
  • the figure 19 illustrates four radial orifices 51 of admission or discharge of the fluid in the external cavities of the machine, these orifices are formed on the outer surface of the stator 2 and radially cross its thickness to open into the outer cavities 8 of the machine.
  • FIGS. 20a to 20c illustrate orifices made in the lateral flanges 12, 13 of closure of the machine, in particular in the form of axial orifices and peripheral lights.
  • two axial orifices 52 allow admission of the fluid axially (in the direction of the longitudinal axis of the machine) inside the rotor, these orifices may advantageously be provided with valves ensuring their closure and respectively their opening.
  • the two lateral flanges 12, 13 are also each provided with four peripheral lights 53 which are slots having a generally half-moon shape, their dimensions and their arrangement being made so that, at least in one of the positions of the rotor 3, these peripheral lights 53 are completely obstructed by the pivoting joints 7 of the rotor 3.
  • the figure 20b illustrates such a position where the four peripheral lights 53 are covered by the four pivoting joints 7 of the rotor 3.
  • the peripheral lights 53 are gradually exposed and the surface of the exchange zone increases with the angle of rotation to a position where they are completely open ( Fig. 20c ), then the section of the fluid exchange zone then decreases to the position illustrated in FIG. figure 20b .
  • This solution provides progressive and automatic opening and closing of the exchange zone between a fluid circuit upstream or downstream of the machine and the external cavities 8 of the machine, all the closures and orifice openings being in phase. between them.
  • FIGS 21a and 21b illustrate another alternative embodiment of the fluid exchange zones inside the machine, in particular via inlet or discharge channels 54 made at the pivoting joints 7 of the rotor 3.
  • the rotation which takes place between the pistons 6 and their pivots 7 allows an opening and an automatic closing of these channels 54 extending radially and to a certain depth along the pivoting joint 7. It is noted that the opening and closing of the channels belonging to two pivoting joints opposing (facing each other) are in phase.
  • the Figures 22a to 22c illustrate another alternative embodiment of the fluid exchange zones, this exchange being done by channels 55 made in a radial direction in the pistons 6.
  • the figure 22a illustrates the rotor 3 of the machine where each piston 6 comprises two through holes, the fluid passage can be made in both directions (inside out and vice versa).
  • the figure 22b illustrates an example of a rotor in which each piston comprises a through orifice made so as to be able to receive a closing valve ensuring the passage of the fluid from the inside to the outside of the rotor (in the direction of the arrows of the fig.22b ).
  • the figure 22c illustrates an example similar to the previous one, but where the passage of the fluid is allowed from the outside towards the inside of the rotor (in the direction of the arrows of the fig.22c ).
  • the figure 23 illustrates another embodiment of axial channel 56 for admission or discharge of fluid, the latter being formed in the central shaft or rotation 57 of the machine.
  • the internal cavity of the rotation shaft 57 comprises a first axial channel 56 whose inlet orifice is at a first end 58 of the shaft and the outlet orifice 59 at the center plane of the machine, and a second axial channel 56 'which starts from this middle plane and goes to the second end 60 of the rotation shaft 57.
  • Orifices preferably provided with valves, allow the admission of the fluid conveyed by the central shaft in the cavities through which it passes, or even the discharge of the fluid from the cavities via the axial channel of the shaft to an external circuit of the machine.
  • the fluid inlet and outlet channels in various cavities of the machine may have so-called free sections (eg orifices, slots or slots) which are successively obstructed, then open when the rotor is rotated, or they may be provided with valves or valves (possibly spring return) actuated opening / closing by a fluid pressure difference, or, in another embodiment, they can be provided with closing / opening devices controlled by electric actuators or electromechanical (eg solenoid valves, controlled valves, etc ).
  • a combination of the means for closing / opening the channels can also be envisaged, for example said free sections may furthermore comprise a controlled device (such as a rotational shutter with controlled rotation) that can, for example, make a variation of the surface of the section. of the exchange zone.
  • the Figures 24 to 28 illustrate a compressor 80 according to one embodiment of the claimed invention, more particularly using two of its external cavities as a water turbine, two of its other external cavities as well as several internal cavities as air pumps, each being able to provide different values of the outlet air pressure, as will be explained later.
  • the main function of the machine is to turbinate water to compress air
  • the water source can be, for example, a running water tap of the conventional distribution network.
  • Ambient air can either be compressed at a higher pressure than water, but at a lower flow rate, or at a higher flow rate, but at a lower pressure.
  • the application is a compressor / inflator intended for bicycle wheels, balloons, beach air mattresses, inflatable beds, or other.
  • the machine illustrated in figure 24 has two left extrados peripheral cavities 14, two extrados straight peripheral cavities 14, four toric cavities 66, and a central cavity 67, which makes an instantaneous total number of 9 cavities, which can fulfill five functions.
  • the figure 24 illustrates a perspective view of the machine, one of the side closure flanges having been removed to leave visible the internal elements of the machine.
  • the machine comprises a stator 2 whose enclosure 1 receives a deformable rhombus rotor 3, whose pivoting articulations 7 are in contact, with or without clearance, with the internal surface of the enclosure 1 during the rotation of the rotor 3 , this being done in the direction indicated by the arrow of the figure 24 .
  • the deformable rhombus 4 comprises four pistons 6 connected to each other by a pivoting joint 7. Each piston 6 defines a peripheral cavity extrados 14 with the inner surface of the stator 2 and two side closure flanges, four extrados peripheral cavities 14 having thus been formed outside the rotor 3.
  • the four pistons 6 are identical, the underside of a piston 6 is provided a protrusion 61 having a general shape toroid portion whose axis of revolution is located in the pivot axis of a joint 7 connecting two pistons 6 adjacent. More particularly, the underside of each piston 6 comprises a plane-shaped connection zone 62 connecting a first pivoting joint 7 on the right to the protrusion 61 of the piston 6.
  • the connection zone 62 is extended by an internal zone 63 of shape concave cylindrical extending by a central zone 65 of generally convex cylindrical shape connected by an outer zone 64 of generally planar shape to the second pivoting joint 7 of the left of the piston 6.
  • each connection zone 62 of this first piston cooperates with an outer zone 64 of a second piston 6 adjacent and which is located on the right with respect to the first, and that each central zone 65 of the first piston cooperates with an inner zone 63 of a third piston, adjacent and located on the left with respect to the first.
  • These zones cooperate so that, at a predetermined position of the rhombus 4, they can fit together and, as the diamond 4 rotates, they can move away and come together and thus form internal cavities with variable volume for receiving a fluid.
  • the zones of the intrados of the pistons 6 thus define five internal cavities of variable volume, including four toric cavities 66 and a central cavity 67.
  • the left side of the extrados peripheral cavities 14 of the machine is used in a water turbine, this is a motor function of the machine.
  • the right side of the extrados peripheral cavities 14 of the machine, more particularly the two other extrados peripheral cavities 14 adjacent, is used as a low pressure air pump.
  • the toric cavities 66 are used as a medium pressure air pump.
  • the central cavity 67 is used as a high pressure air pump.
  • the management of the transfer of compressed air between the different cavities is done via valves: when the need for pressure is low, it is desired to use the different pumps (constituted by the right part, the toric cavities and the central cavity) in parallel ; or when the need for pressure is high, the pumps are used in series.
  • the machine is autonomous and operates without mechanical transmission shaft. Indeed, there is a balance between the energy supplied by the turbined fluid and the compressed gas.
  • the stator 2 is a vessel having a bottom wall 68, its enclosure 1 being closed by a lateral flange 12.
  • the stator 2 is closed by the flange 12 by means of the fastening screws passing through the passages 69 made on the periphery of the stator 2 and the lateral flange 12.
  • the bottom wall 68 of the stator comprises four hollow cells arranged on its periphery and having a half-moon shape and each extending through an axial channel 75 opening into an extrados cavity 14.
  • the bottom wall 68 comprises: an air inlet half-moon 71, an air discharge half-moon 72, a water intake half-moon 73 and a water discharge half-moon 74.
  • the bottom wall 68 also comprises, at the level of the area covered by the rotor, four distribution windows, two air intake windows 76 in the toric cavities 66 and two air discharge windows 77 in the cavities.
  • the bottom wall 68 also comprises, in its central zone, two air intake recesses 79 and two air outlet recesses 78 cooperating with the central cavity 67.
  • the connections with fluid circulation ducts (FIG. pipes, connection hoses, etc.) are represented by circles (better visible in the figure 26 ) inside each inlet zone, respectively discharge of the wall 68.
  • the figure 28a illustrates the compressor 80 in the most crushed position of the diamond 4, two opposing toric cavities 66 are at their maximum volume and the other two at their minimum volume, the central cavity 67 is at its minimum volume and the extrados peripheral cavities 14 are in intermediate position.
  • the figure 28b illustrates the compressor 80 in the position in which the rhombus 4 tends to the shape of a square.
  • the toric cavities 66 begin the discharge of the air (left and right) and suction (up and down).
  • the central cavity 67 begins to suck and the extrados peripheral cavities 14 are at the end of aspiration (up and down) and at the beginning of discharge (left and right).
  • the figure 28c illustrates a following phase of the rotation of the diamond, which has taken the form of a square, where the toric cavities 66 continue the aspiration of the fluid (up and down) and the discharge (left and right) , the central cavity 67 has reached its maximum volume and the extrados peripheral cavities 14 have finished the aspiration (up and down) and the discharge (left and right).
  • the figure 28d illustrates a next phase where the toric cavities 66 end the suction of the fluid (upper right and lower left) and the discharge (top left and bottom right), the central cavity 67 is in full discharge and the extrados peripheral cavities 14 begin the discharge (up and down) and suction (left and right).
  • Such a compressor 80 is when it receives, at the entrance, the power by turbining the water of the conventional adduction network and that it sends, in discharge, compressed air.
  • the flow of water received with a value of about 10 Umin is turbined by a pressure of 2 bar absolute at atmospheric pressure (operation at the standard network pressure of 3 bar relative is also possible).
  • the machine uses two of the four peripheral cavities 14 (upper left and upper right) which are formed by the upper surface of the piston 6 and the inner surface of the stator 2. The other cavities are used for the pumping of the air.
  • the power received by the machine is then absorbed by the various integrated pumps that compress the air from the atmospheric pressure to the downstream pressure.
  • the various pumps will be in charge or short-circuited according to the pressure requirements downstream of the machine.
  • the balance between the power received and the power consumed is without a motor shaft. Indeed, if the pressure requirement is low (beginning of the inflation, the pressure is mainly due to the pressure drops), then all the pumps will be in charge and the flow rate is maximum.
  • the flow rate of all the pumps is then approximately 30 NL / min (normal liters per minute), ie 10 NL / min for the extrados cavities 14 reserved for pumping air, 16 NL / min for toric cavities 66 and 4 NL / min for the central cavity 67, for an overpressure of up to 0.3 bar.
  • the toric cavities 66 are short-circuited and the flow rate decreases in favor of the pressure.
  • the flow rate of all the pumps is then about 14 NL / min (10 NL / min for the extrados peripheral cavities 14 reserved for pumping the air and 4 NL / min for the central cavity 67) for an overpressure from up to 0.6 bar.
  • the inflation at maximum pressure is also bypassing the extrados peripheral cavities 14 of the pump, to keep only the water turbine and the central cavity 67.
  • the flow of the central cavity 67 is about 4 NL. / min for an overpressure up to 2 bar or about 3 bar absolute.
  • the machine When the diamond is in the particular configuration where it forms a square ( fig.28c ), the machine is in a neutral position. To make this position unstable, it is possible to use an actuating device (such as a device with springs arranged between two associated pistons or with magnets integrated in the pistons) in order to promote the displacement towards the most crushed position of the rhombus.
  • an actuating device such as a device with springs arranged between two associated pistons or with magnets integrated in the pistons
  • the technical characteristics of the machine are given below as an example.
  • the machine has a very compact size. Indeed, the length (along the long axis of the stator cross section) is about 70 mm, the width (along the minor axis of the stator cross section) is about 60 mm and the depth (according to the longitudinal axis) is about 40 mm.
  • An improved, more compact and lighter machine can be designed for higher rotational speeds, while providing it with sealing systems at its fluid exchange zones.
  • the dimensional and geometric tolerances are of the order of a hundredth of a millimeter in order to limit leaks.
  • the maximum volume of an extrados peripheral cavity 14 is about 5 cm 3
  • that of a toric cavity 66 is about 4 cm 3 and that of the central cavity 67 of 2 cm 3 .
  • the dead volume of an extrados peripheral cavity 14 is negligible and depends essentially on the inlet and outlet pipes, ie about 0.1 cm 3 for a pipe of the air pump and 1 cm 3 for a pipe of the water turbine.
  • the dead volume of a toric cavity 66 is negligible and also essentially depends on the inlet and outlet pipes, ie approximately 0.1 cm 3 .
  • the central cavity 67 has a dead volume which also depends on the shape of the cavity, but which can be reduced to about 0.2 cm 3 .
  • the machine is waterproof vis-a-vis from the outside because it is satisfied with static seals (no relative movement of parts).
  • the internal sealing of the machine is essentially by reduced clearance, large areas of lamination of leaks and the use of deformations of pressurized parts to reduce play and improve sealing.
  • the machine can be made with plastic materials with a low coefficient of friction to ensure the lightness of the assembly, because the pressure is low and the parts have a very robust design.
  • the machine can cope with water problems in air pumps, thanks in particular to dead volumes, which serve as pneumatic dampers to prevent hydraulic shock when the volume decreases.
  • the pressure increasing strongly, the pistons and the flanges deform to release a fluid passage.
  • the compressor 80 is designed to rotate at 500 rpm for a water flow of 10 Umin.
  • the machine can operate with water at a temperature between 10 and 60 ° C, in an ambient air between 10 and 50 ° C and with air or water very polluted (size and concentration of the high particles, being able to for example, containing sand particles), the machine being equipped with filters upstream of the water supply and upstream of the air supply, making it possible to filter the particles in these fluids of a size greater than 20 microns.
  • the passage of water in the device to be inflated is avoided thanks to a small vertical pipe directed upwards right out of the machine. This device allows the droplets of water in the air to fall; but do not hinder the passage of air. This portion of pipe can be connected to the water inlet to empty this pipe automatically. This pipe is not shown in the figures, and the short-circuiting systems are not shown.
  • the machine illustrated in Figures 24 to 28 can also function as a compressor with several stages of compression.
  • a machine MRLD according to the invention with an outside diameter of 250 mm and a depth of 140 mm (according to the invention). longitudinal axis of the machine), can accommodate displacements per revolution of 1.022 cm 3 for the first compression stage, 680 cm 3 for the second compression stage and 102 cm 3 for the third compression stage, of the same fluid successively passing through the extrados peripheral cavities 14, the toric cavities 66 and the central cavity 67.
  • Such a three-stage compressor (or multicompressor) according to the invention has a bulk volume of 6.872 cm 3 .
  • a device composed of 3 MRLD machines known from the state of the art, each operating as a compressor to individually fulfill one of the three compression functions of the three-stage machine, having identical tower capacities but n 'operator that the external cavities, would have a volume of space of 14.120 cm 3 , if it was made according to construction characteristics similar to the compressor MRLD tri-tier of the invention.
  • the MRLD machine according to the invention incorporating three compression functions in the same rotor, has a power density 2.05 times greater than a device composed of three MRLD machines known from the state of the art.
  • the implementation of several different MRLD machines, as known in the state of the art, to perform a function (for example compression or expansion on a compressible fluid), when this function must necessarily be segmented into several successive functions of the same nature, because of the large extent of the variation of at least one of the parameters of the fluid (typically for pressure ratios greater than 10) or for an objective of improving the yield, can now be performed by a single machine MRLD according to the invention.
  • the invention provides answers in many applications, in particular so-called mobile or on-board applications, which have as their primary technical criteria the reduction in size and / or mass.
  • FIGS. Figures 24 to 28 Another example of application of the machine of the invention whose structure is illustrated in FIGS. Figures 24 to 28 is described in the following. It is a converter of hydraulic energy into autonomous pneumatic energy without transmission. It can ensure the local production of compressed air without the use of a compressor. This feature is very relevant to the end of a hydraulic boom boom on which one would like to install a pneumatic shock system.
  • the oil provides a sealing barrier between the two compression stages. Pneumatic application in closed circuit avoids the pollution of the air. It is very easy to separate the oil and the air and to reintegrate the oil in the circuit via an automatic purge system. The small amount of air in the oil is not a pollutant for the oil and does not have any major consequences because the air will separate from the oil during settling in the tank.
  • the machine thus produced does not require a mechanical transmission shaft.
  • the power generated by the turbining of the oil is absorbed by the compression of the air. Turbining and compression are simultaneous (parallel operation) while the two stages of compression are successively (for series operation).

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)

Claims (15)

  1. Rotationsmaschine mit verformbarem Rhombus, aufweisend ein Gehäuse (1), das einen Stator (2) bildet, der geeignet ist, einen Rotor (3) aufzunehmen, bei dem es sich um einen verformbaren Rhombus (4) handelt, der sich mit oder ohne Spiel in Kontakt mit der Innenfläche des Gehäuses (1) befindet, wobei der verformbare Rhombus (4) mehrere Kolben (6), und bevorzugt vier Kolben aufweist, die nacheinander verbunden sind über ein Drehgelenk (7) der Achse parallel zur Längsachse des Gehäuses (1) verläuft, und die auf diese Weise eine geschlossene Kette bilden; wobei jeder Kolben (6) eine äußere Seite, genannt Außenseite, und eine innere Seite, genannt Innenseite, aufweist; wobei die Innenfläche des Gehäuses (1) der Maschine mindestens einen so genannten externen Hohlraum (8) mit der äußeren Seite des verformbaren Rhombus (4) und mit den seitlichen Abschlusswänden des Gehäuses definiert, und mindestens einen so genannten internen Hohlraum (10) definiert, der im Innern des Rotors mit den seitlichen Abschlusswänden des Gehäuses (1) gebildet wird; wobei mindestens einer der externen Hohlräume (8) und/oder mindestens einer der internen Hohlräume (10), direkt oder indirekt, am Einlass mindestens eines Fluidkreislaufs außerhalb der Maschine verbunden ist, wobei die Maschine dadurch gekennzeichnet ist, dass die externen (8) und internen (10) Hohlräume zusammen mindestens drei Hohlräume mit variablem Volumen aufweisen, die mindestens drei verschiedene Funktionen gleichzeitig oder mindestens drei identische Funktionen nacheinander oder mindestens drei Funktionen erfüllen, von denen mindestens eine von den beiden anderen verschieden ist und gleichzeitig mit den beiden anderen Funktionen ausgeführt wird, die identisch sind und nacheinander ausgeführt werden, und dadurch, dass die Innenseite jedes Kolbens (6) mit einer Protuberanz (61) versehen ist, wobei jede Protuberanz (61) mit der Protuberanz (61) der beiden benachbarten Kolben (6) derart zusammenwirkt, dass mindestens zwei innere Hohlräume (10) mit variablem Volumen erzeugt werden;
    wobei jede der Funktionen ausgewählt ist aus: Verbrennungsmotor, Turbine, Verdichter, Pumpe, Dosiergerät, Mischer, Mengenteiler, Energiewandler, Brecher, um mindestens einen der Parameter des aus der Maschine austretenden Fluids bezogen auf das eintretende Fluid zu modifizieren.
  2. Maschine nach Anspruch 1, dadurch gekennzeichnet, dass sie als Maschine mit mehreren Pumpen und/oder als Maschine mit mehreren Turbinen und/oder als Maschine mit mehreren Verdichtern arbeitet.
  3. Maschine nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass sie Mittel zur Übertragung von Fluid von einem Hohlraum mit variablem Volumen zum nächsten aufweist.
  4. Maschine nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, dass es sich bei den externen Hohlräumen (8) um periphere Außenhohlräume (14) handelt, wobei jeder zwischen der Außenseite (9) eines Kolbens (6), der Innenfläche des Gehäuses (1) und den seitlichen Abschlussflanschen (12, 13) definiert ist.
  5. Maschine nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, dass es sich bei den externen Hohlräumen (8) um kreisförmige Außenhohlräume (15) handelt, wobei jeder durch die Außenseiten (9) der beiden benachbarten Kolben (6), das Drehgelenk (7), das sie verbindet, die Innenfläche des Gehäuses (1), die in diesem Fall kreisförmig oder ellipsenförmig ist, und die seitlichen Abschlussflansche (12, 13) definiert ist.
  6. Maschine nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass ein interner Hohlraum (10) derart ausgeführt ist, dass er mindestens eine gemeinsame Fläche mit der Innenseite (11) mindestens eines der Kolben (6) und/oder mit der Innenseite mindestens eines der Drehgelenke (7) und/oder mit mindestens einem Zwischenstück aufweist, das mit einem der Kolben (6) oder mit einem der Drehgelenke (7) verbunden ist.
  7. Maschine nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass mindestens zwei der peripheren, externen Hohlräume (8) oder mindestens zwei der internen Hohlräume (10) oder mindestens zwei der externen (8) und internen (10) Hohlräume ein anderes Fluid transportieren.
  8. Maschine nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass sie Fluidaustauschzonen mit den externen Hohlräumen (8) aufweist, wobei diese Zonen Kanäle sind, die in den Kolben (6), den Gelenken (7), den Flanschen (12, 13), dem Profil des Gehäuses (1) oder der Übertragungsvorrichtung ausgebildet sind.
  9. Maschine nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass sie Fluidaustauschzonen mit den internen Hohlräumen (10) aufweist, wobei diese Zonen Kanäle sind, die in den Kolben (6), den Gelenken (7), den Flanschen (12, 13) oder der Mittelachse (57) oder allgemeiner der Übertragungsvorrichtung der Maschine ausgebildet sind.
  10. Maschine nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass ihre Funktion umkehrbar ist.
  11. Maschine nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass die Innenseiten der Kolben fünf interne Hohlräume mit variablem Volumen definieren.
  12. Pumpe, aufweisend eine Rotationsmaschine nach einem der Ansprüche 1 bis 11.
  13. Turbopumpe, aufweisend eine Rotationsmaschine nach einem der Ansprüche 1 bis 11.
  14. Motor, aufweisend eine Rotationsmaschine nach einem der Ansprüche 1 bis 11.
  15. Verdichter, aufweisend eine Rotationsmaschine nach einem der Ansprüche 1 bis 11.
EP09741330.6A 2008-09-22 2009-09-22 Mehrfunktionsrotationsmaschine mit verformbarem rhombus Not-in-force EP2334906B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP16151876.6A EP3045656B1 (de) 2008-09-22 2009-09-22 Mehrfunktionsrotationsmaschine mit verformbarem rhombus

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR0805177A FR2936272B1 (fr) 2008-09-22 2008-09-22 Machine rotative a losange deformable multifonctions
PCT/FR2009/001119 WO2010031927A1 (fr) 2008-09-22 2009-09-22 Machine rotative a losange deformable multifonctions

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EP2334906B1 true EP2334906B1 (de) 2016-01-27

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN108708852A (zh) * 2018-05-30 2018-10-26 安徽美芝精密制造有限公司 活塞、压缩机和制冷设备以及活塞的制备方法

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR3005106B1 (fr) 2013-04-25 2017-11-24 Jean Pierre Ambert Machine volumique rotative a trois pistons

Family Cites Families (27)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3196854A (en) 1963-04-08 1965-07-27 Novak Andrew Rotary engine
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
US3387596A (en) * 1965-06-09 1968-06-11 Politechnika Warszawska Combustion engine with revoluting pistons forming a closed kinematic chain
ES393065A1 (es) 1971-07-08 1973-08-16 Martin Artajo Maquina de embolo rotativo y culatas oscilantes.
DE2145768A1 (de) * 1971-09-14 1973-03-29 Willy Rudolf Christia Foerster Gleit-druck-kolben fuer rotationskilbenpumpe, rotationskolben-kompressor (arbeitsmaschinen) und rotationskolben-verbrennungsmotor (kraftmaschinen)
CA997998A (en) 1974-08-02 1976-10-05 Ernest A. Steinbrink Rhombo-rotary engine
FR2493397A1 (fr) 1980-11-03 1982-05-07 Ambert Jean Pierre Moteur rotatif
IT1180993B (it) * 1984-06-22 1987-09-23 Italo Contiero Macchina volumetrica rotativa
US5288217A (en) * 1986-12-30 1994-02-22 Italo Contiero Cyclic volume machine
FR2687728B1 (fr) * 1992-02-21 1994-04-29 Antonov Roumen Machine volumetrique a pistons louvoyants, en particulier moteur a quatre temps.
DE19639503C1 (de) * 1996-09-26 1998-01-15 Herbert Huettlin Schwenkkolbenmaschine
US6164263A (en) * 1997-12-02 2000-12-26 Saint-Hilaire; Roxan Quasiturbine zero vibration-continuous combustion rotary engine compressor or pump
CO5130041A1 (es) 1999-09-08 2002-02-27 Talero John Alejandro Sanchez Motor rotatorio de combustion interna (turbovolante)
DE10001962B4 (de) * 2000-01-18 2004-07-22 Hüttlin, Herbert, Dr.h.c. Rotationskolbenmaschine
WO2001088341A1 (en) 2000-05-12 2001-11-22 Peter Szorenyi Hinged rotor internal combustion engine
AU726791B1 (en) * 2000-05-12 2000-11-23 Peter A. Szorenyi Hinged rotor internal combustion engine
CA2310488A1 (fr) 2000-05-23 2001-11-23 Normand Beaudoin Polyturbine energetique et antirefoulement
EP1309776A4 (de) * 2001-05-26 2006-12-06 Dong Hyun Kim Rotationsmaschine
US7178502B2 (en) 2001-06-05 2007-02-20 Paul D. Okulov Balanced rotary internal combustion engine or cycling volume machine
US6899075B2 (en) * 2002-03-22 2005-05-31 Roxan Saint-Hilaire Quasiturbine (Qurbine) rotor with central annular support and ventilation
MXPA05009639A (es) 2003-02-10 2006-02-08 Gilles Saint-Hilaire Motor rotativo.
US20050260092A1 (en) * 2003-10-29 2005-11-24 Bolger Stephen R Turbostatic compressor, pump, turbine and hydraulic motor and method of its operation
FR2911631A1 (fr) * 2007-01-19 2008-07-25 Philippe Kuzdzal Moteur rotatif a losange deformable
FR2938291B1 (fr) * 2008-11-12 2010-11-12 Vincent Genissieux Machine rotative a losange deformable comportant un mecanisme de transmission perfectionne.
CA2768255C (en) * 2009-07-22 2017-07-11 Gullivert Technologies Inc. Blade support in a quasiturbine pump
US8904991B2 (en) * 2012-11-19 2014-12-09 Kuwait University Rotary mechanism with articulating rotor

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN108708852A (zh) * 2018-05-30 2018-10-26 安徽美芝精密制造有限公司 活塞、压缩机和制冷设备以及活塞的制备方法

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EP3045656B1 (de) 2017-12-20
US20110236240A1 (en) 2011-09-29
DK2334906T3 (en) 2016-05-02
FR2936272B1 (fr) 2012-07-13
US9523276B2 (en) 2016-12-20
WO2010031927A1 (fr) 2010-03-25
FR2936272A1 (fr) 2010-03-26
EP3045656A1 (de) 2016-07-20
EP2334906A1 (de) 2011-06-22

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