EP3256695B1 - Antriebs-oder arbeitsmaschine mit ausgleichsanordnung - Google Patents

Antriebs-oder arbeitsmaschine mit ausgleichsanordnung Download PDF

Info

Publication number
EP3256695B1
EP3256695B1 EP16716277.5A EP16716277A EP3256695B1 EP 3256695 B1 EP3256695 B1 EP 3256695B1 EP 16716277 A EP16716277 A EP 16716277A EP 3256695 B1 EP3256695 B1 EP 3256695B1
Authority
EP
European Patent Office
Prior art keywords
rotor
stator
recess
machine
axis
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP16716277.5A
Other languages
English (en)
French (fr)
Other versions
EP3256695A1 (de
Inventor
Ledis MESSORI
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Cbf Srl
Original Assignee
Cbf Srl
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Cbf Srl filed Critical Cbf Srl
Publication of EP3256695A1 publication Critical patent/EP3256695A1/de
Application granted granted Critical
Publication of EP3256695B1 publication Critical patent/EP3256695B1/de
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/10—Outer members for co-operation with rotary pistons; Casings
    • F01C21/104—Stators; Members defining the outer boundaries of the working chamber
    • F01C21/108—Stators; Members defining the outer boundaries of the working chamber with an axial surface, e.g. side plates
    • 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
    • F01C1/22—Rotary-piston machines or engines of internal-axis type with equidirectional movement of co-operating members at the points of engagement, or with one of the co-operating members being stationary, the inner member having more teeth or tooth- equivalents than the outer member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C19/00—Sealing arrangements in rotary-piston machines or engines
    • F01C19/02—Radially-movable sealings for working fluids
    • 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
    • F01C19/00—Sealing arrangements in rotary-piston machines or engines
    • F01C19/08—Axially-movable sealings for working fluids
    • 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
    • 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
    • F04C2240/00—Components
    • F04C2240/20—Rotors

Definitions

  • the invention relates to a driving motor or working machine which is able to convert the energy of a fluid into energy of the mechanical type or deliver energy, e.g. mechanical energy, to a fluid.
  • energy e.g. mechanical energy
  • the invention particularly relates to the geometric conformation of the driving motor or working machine.
  • the invention particularly refers to a driving motor or working machine of the rotary type, i.e. with its movable parts essentially moving according to a rotary movement, more precisely according to a roto-orbital movement, which provides at least a stationary part of the machine, termed stator, and a movable portion, called rotor which interacts with the stator.
  • the invention finds effective use in many different sectors providing use of an endothermic engine, i.e. a machine configured for conducting a fluid transformation thermodynamic process.
  • an endothermic engine i.e. a machine configured for conducting a fluid transformation thermodynamic process.
  • the areas of greatest use are therefore the automotive and motorcycle industry, the electric generators actuation sector, or the sector concerned with professional implements provided with an endothermic engine and the like.
  • a further area of application of the present invention is that of the plants and/or industrial machinery, wherein use of hydraulic pumps or hydraulic motors is provided.
  • Wankel engine which comprises a rotor and a stator chamber, which stator chamber is capable of accommodating the rotor that is moving therein according to a roto-orbital movement.
  • the rotor of the Wankel engine is applicable to the pistons, while the stator chamber is applicable to the cylinders inside of which the pistons are sliding alternately.
  • stator chamber of the Wankel engine is symmetrical relative to the two orthogonal barycentric axes and exhibits two lobed-shaped recesses capable of receiving the rotor during operation of the motor.
  • the configuration of the two-lobes stator chamber is the most widespread and is known as epitrochoidal-shaped chamber.
  • the rotor is instead equilateral triangular in shape, with slightly convex and converging sides at the vertices of the triangle in three distinct apical zones.
  • the contact between stator and rotor occurs at the apical segments placed relative to the vertices of the rotor which are sliding on the walls of the stator.
  • stator On the walls of the stator there are generally arranged openings for the suction of a fuel-air mixture and the discharge of the burnt gases. Seats are further provided which accomodate one or more mixture spark plugs.
  • the rotor turning inside the stator chamber according to a specific orbiting movement, forms three chambers, the volume of which varies cyclically: i.e. inside the three chambers, three with four-stroke provided Otto cycles occur simultaneously, which cycles are out of phase by 120°. Because for each revolution of the rotor, three with four-stroke provided Otto cycles are completed, it follows that at each revolution of the drive shaft a cycle becomes completed.
  • the rotor centrally exhibits a through hole inside of which a ring gear is arranged, which is predisposed for engaging with a pinion that is keyed on the stator of the Wankel engine.
  • the drive shaft features a stationary axis of rotation about which the rotor is moving according to a roto-orbital movement, as already mentioned.
  • Wankel endothermic engine is nowadays used for application to some car models and can further be applied in the aviation industry, or even in the dynamic model sector, proposed on a reduced scale but thoroughly working.
  • Wankel engine Uses of the Wankel engine are however rather limited in that this type of engine exhibits several drawbacks.
  • the main drawbacks of the Wankel engine are particularly due to the presence of apical segments, which are poorly reliable, breakable and tend to cause leaks. Further, because of the angular conformation of the rotor, the rotor is subject to sliding and to micro-impact shocks against the wall of the stator, the sliding track of which deteriorates quickly, thereby being tightness of the gaskets reduced with consequent reduction in efficiency.
  • US 5391067 discloses a fluid displacement rotary device free of any feed gears between the rotor and the corresponding crankshaft or the stator case.
  • DE 3508072 discloses a planetary compressor corresponding to a positive displacement pump for gases or liquids, which planetary compressor is provided with an elongated hole having an internal toothing, which may be regarded as an internal stationary gear wheel.
  • US 2011/0209477 discloses a rotary displacement system which may be used to compress and/or expand compressible fluids.
  • US 2014/0134035 discloses a system comprising a trochoidal rotary device, provided with a rotor and a shaft which is eccentrically connected to the rotor, the shaft being stationary with respect to the rotor.
  • US 3999905 discloses a rotary motor provided with a rotor having a plurality of apices. The apices are provided with sealings which are pushed against the walls of a chamber wherein the rotor is housed.
  • the driving motor or working machine is so devised as to simplify the mechanical construction of the machine itself, thereby being the components number thereof simultaneously reduced.
  • the invention allows to overcome the drawbacks previously mentioned in connection to the Wankel engine.
  • the rotor indeed is interacting with the stator at the rolling elements, which rolling elements are rolling without sliding against the inner surface of the stator recess and remain in contact with such surface in any position assumed by the rotor, while the rotor is moving by rotating about the recess axis and rotating simultaneously about its own axis.
  • apical segments of the Wankel engine can be removed, which apical segments may result in tightness problems, poor reliability and fragility.
  • the profile of the stator's inner recess is indeed so designed as to ensure a tangency condition between the rolling elements and the inner surface of the stator in all positions taken on by the rotor during its rotary-orbital movement. This ensures that the rotor can move in contact with the inner surface of the stator recess, without the protrusions of the rotor sliding against this surface or becoming detached therefrom. It is further ensured that the rolling elements engage sealingly with the inner surface which defines the stator recess.
  • the machine according to the invention is provided with a rotor which is freely sliding along the eccentric portion of the shaft on which the rotor is mounted.
  • the rotor is axially balanced by hydraulic forces, i.e. by forces exerted by a pressurized fluid which is acting on two opposite faces of the rotor.
  • the machine is configured such that the resultant of the forces which are acting on the rotor and following a direction parallel to the axis of the rotor, is substantially equal to zero.
  • the pressurized fluid sent towards the two opposite faces of the rotor allows to provide a hydraulic floating of the rotor inside the stator.
  • this balancing system uses the same working fluid to which the machine is configured for transferring energy or by which the machine is configured for receiving energy.
  • the machine 1 can be a driving motor or a working machine that is suitable to convert the energy of a fluid into energy of a mechanical type or to impart energy, for example mechanical energy, to a fluid and vice versa.
  • the machine in accordance with the present invention may be a machine configured for transferring energy to a fluid, or a machine configured for receiving energy from a fluid.
  • the machine 1 may be an endothermic engine or a hydraulic motor, in the case where it is configured as a driving motor.
  • the machine 1 can be a hydraulic pump, in the case where it is configured as a working machine.
  • the machine 1 comprises a rotor 10 having a preset n number of end zones or vertices 11.
  • a rotor 10 having a preset n number of end zones or vertices 11.
  • n is a positive integer greater than one, or equal to one, as better detailed below.
  • the rotor 10 is further provided with n sides 14 each of which is interposed between two vertices 11.
  • the sides 14 may be so configured as to confer a regular shape to the rotor 10.
  • the sides 14 may be equal to one another and be, for example, convex-shaped.
  • a rolling element 16 is disposed, which is particularly shaped as a roller.
  • Each rolling element 16 is free to rotate about an axis passing through the corresponding vertex 11.
  • the number of the rolling elements 16 of the rotor 10 is equal to the number of vertices 11, i.e. it is equal to n.
  • the machine 1 is further provided with a stator 20 comprising a stator case 25 inside of which a recess 21 is afforded. Within the recess 21 there are defined n-1 lobes 22, namely n-1 recesses separated from one another by respective protuberances 29. The number of lobes 22 of the stator 20 is therefore equal to the number of vertices 11 of the rotor 10, reduced by one.
  • the number of lobes 22 of the stator 20 is equal to two.
  • the lobes 22 of the stator 20 are regularly distributed about an axis A1 of the stator 20, which can be regarded as an axis of symmetry of the recess 21.
  • the axis A1 of the stator 20 coincides with the axis of the machine shaft 1.
  • the rotor 10 is mounted eccentrically inside the recess 21 of the stator 20.
  • the axis A1 of the stator 20 does not coincide with the central axis A2 of the rotor 10.
  • the central axis A2 of the rotor 10 is placed at a distance E from the axis A1 of the stator 20. The distance E therefore defines the eccentricity of the rotor 10 relative to the stator 20.
  • the rotor 10 is movable with a roto-orbital movement relative to the stator 20.
  • the rotor 10 is rotating about its central axis A2, and is simultaneously orbiting about the axis A1 of the stator 20.
  • a cylinder with radius E is described about the axis A1 of the stator 20 by the central axis A2 of the rotor.
  • a plurality of working volumes 40 is defined between the stator 20 and the rotor 10.
  • the working volumes 40 may exhibit different pressure and temperature conditions, as well as different fluids.
  • the recess 21 of the stator 20 is defined by an inner surface 22a which is so conformed as to interact with the rolling elements 16 in such a manner that each rolling element 16 may roll without sliding against the inner surface 22a.
  • the inner surface 22a is so devised as to accommodate the rotor 10, which is provided with the rolling elements 16, so that the rolling elements 16 are steadily in contact with the inner surface 22a while the rotor 10 is moving about the axis A1 of the stator 20, thus orbiting about said axis and simultaneously rotating about its own central axis A2.
  • a traditional Wankel engine would be provided with a two-lobes stator having an inner recess defined by a curve termed epitrochoid, which curve is drawn by a generic point Q, placed at a distance E from the center of a circumference with radius R (rolling circumference), when the latter is rolling on a circumference with radius 2R (base circumference).
  • epitrochoid which curve is drawn by a generic point Q, placed at a distance E from the center of a circumference with radius R (rolling circumference), when the latter is rolling on a circumference with radius 2R (base circumference).
  • Cartesian reference system having an origin O which coincides with the center of the base circumference.
  • O1 it is signified the center of the rolling circumference that is rolling on the base circumference.
  • the X-axis of the Cartesian reference system is identified by the straight line passing through the centers O and O1, respectively of the base circumference and the rolling circumference when the rolling circumference is in a position corresponding to a rotation angle equal to zero with respect to the base circumference.
  • the epitrochoid having the equations mentioned above, defines a stator recess capable of housing a rotor whose vertices identify an equilateral triangle with side 2Tcos ⁇ / 6.
  • the shape of the curve which defines the inner surface 22a of the recess 21 can be derived from the equations which were previously reported by symmetry.
  • the curve which defines the stator recess 21 can be derived by symmetry with respect to the axis A1 from the one already obtained by exploiting above equations.
  • the stator is in this case provided with a recess defined by an inner surface having a circular cross section.
  • n a positive integer, greater than, or equal to one
  • the recess 21 of the stator 20 is defined by a perimetric edge 24, whose x and y coordinates are defined by the above equations, wherein there are present four parameters that can be chosen arbitrarily, i.e. n, R, E, Rr. Once set such parameters, the shape of the stator recess 21 is uniquely defined, as well as the main geometric and dimensional characteristics of the rotor 10 associated therewith.
  • the sides 14 of the rotor 10 which shape can be chosen arbitrarily while taking care to ensure that, during rotation of the rotor 10, the sides 14 do not come into contact with the inner surface 22a of the stator recess 21.
  • the sides 14 may be curve-shaped and may for example be shaped in plan view, as circumferential arcs.
  • the shape of the sides 14 helps to define the shape of the working volumes 40, particularly at the upper dead point. Where the machine 1 is an endothermic engine, the shape of the sides 14 defines the compression ratio.
  • the number of working volumes 40 is equal to n, i.e. equal to the number of vertices 11 of the rotor 10.
  • the stator 20 exhibits a plurality of openings situated within the recess 21, which openings particularly comprise an inlet opening 23a and an outlet opening 23b.
  • openings 23a, 23b depends on the type of configuration of the machine 1 and shall be detailed more fully herein below.
  • the number of openings 23a, 23b is generally equal to (n-1), where n was previously already defined. This condition is particularly applicable to the case in which n is an even number.
  • the machine 1 further comprises a shaft 30, which is rotatable about an axis of rotation which coincides with the axis A1 of the stator 20.
  • the shaft 30 is provided with an eccentric portion 32, configured to be received internally of a hole 12, which hole 12 is formed within the rotor 10 coaxially with the central axis A2 of the rotor 10.
  • the rotor 10 is mounted in such a manner as to be neutral, i.e. free to rotate with respect to the eccentric portion 32 of the shaft 30. Furthermore, the rotor 10 is axially free relative to the shaft 30, i.e. it is free to slide axially along the eccentric portion 32. This means that the eccentric portion 32 is not provided with fastening elements capable of constraining the movement of the rotor 10 along the central axis A2.
  • the coupling between the eccentric portion 32 of the shaft 30 and the rotor 10 can be realized by means of a suitably lubricated bushing.
  • each seat 17 is symmetrical with respect to a radial half-line 18 having its origin in the central axis A2 of the rotor 10 and passing through a respective vertex 11.
  • Each seat 17 is formed as a prismatic-shaped recess, which prismatic-shaped recess is defined by two guide surfaces 17a that are planar and parallel to the respective radial half-line 18.
  • Each rolling element 16 comprises a roller 16a, which in the example shown is supported by a sliding block 16b which is received internally of a corresponding seat 17. Each roller 16a is free to rotate with respect to the sliding block 16b supporting it.
  • each roller 16a is so configured as to be in contact with the inner surface 22a of the recess 21 and to rotate about an own axis so as to move on this surface according to a rolling movement.
  • Each sliding block 16b has a prismatic shape, so as to engage in shape-coupling within the respective seat 17.
  • Each sliding block 16b exhibits a recess 16c in its own outer portion, the recess 16c being suitable for housing at least partially the respective roller 16a.
  • the recess 16c is such as to allow the roller 16a to freely rotate while promoting containment thereof, preferably by carrying on a lateral containment of the roller 16a.
  • the outer portion 16b of the sliding blocks is to be meant as the sliding block portion 16b facing radially outwards, i.e. away from the central axis A2 of the rotor 10.
  • Each sliding block 16b further exhibits an inner portion opposite to the outer portion, i.e. facing towards the central axis A2 of the rotor 10.
  • each sliding block 16b is defined by a thrust surface 16d the function of which will be better described hereinafter.
  • a groove 16f is formed which extends between a front face and a rear face of the sliding block 16b.
  • the front face and the rear face of the sliding block 16b define the sliding block 16b transversely, in particular perpendicularly, to the central axis A2.
  • the groove 16f extends parallel to the central axis A2.
  • Each sliding block 16b is finally provided with one or more lubrication holes 16e, which are conformed as through holes that bring into fluid communication the notch 16c with the groove 16f.
  • the lubrication holes 16e may be conformed as radial holes parallel to one another starting from the groove 16f and flowing into the notch 16c.
  • each sliding block 16b exhibits three lubrication holes 16e.
  • the rotor 10 exhibits channels 19 which are capable of receiving a fluid for the reasons that will be described in detail below.
  • the channels 19 are two in number and are disposed symmetrically relative to a transverse plane of symmetry of the rotor 10, i.e. relative to a plane which extends perpendicularly to the central axis A2.
  • the front face and the rear face of the rotor 10 define the rotor 10 transversely, in particular perpendicularly with respect the central axis A2.
  • the front face and the rear face of the rotor 10 are equal to each other.
  • each channel 19 has an inner edge 19a having for example a circular shape coaxial to the central axis A2.
  • Each channel 19 further exhibits an outer edge 19b which diverges from the inner edge 19a in proximity to the vertices 11.
  • each channel 19 widens towards the vertices 11, so that the seats 17 of the rotor 10 are put in fluid communication with one another.
  • the channel 19 formed on the front face of the rotor 10 is in fluid communication with the channel 19 formed on the rear face of the rotor 10 through the grooves 16f.
  • the grooves 16f of the sliding blocks 16b allow the fluid to flow from one side to the opposite side of the rotor 10, so that any decompensation in the fluid pressure is balanced from one side to the other of the assembly comprising the rotor 10 and the stator 20 in an operating configuration of the machine 1.
  • a pressurized fluid coming for example from an inner flow device of the machine (as for example a mechanical pump, not shown) is sent into a channel 19 of the rotor 10, for example into the channel 19 formed on the rear face of the rotor 10. From the channel 19, the pressurized fluid reaches the seats 17 of the rotor 10, wherefrom it flows into the channel through the grooves 16f, which channel is afforded on the other face of the rotor 10, e.g. on the front face.
  • the pressurized fluid circulating in the channels 19 exerts, on the thrust surfaces 16d of the sliding block 16b, a thrust which is radially directed outwardly of the rotor 10.
  • the rollers 16a are thus pressed against a portion of the inner surface 22a of the recess 21 in an operating configuration the machine 1.
  • the lubrication holes 16e can therefore be regarded as lubricating means which allow the pressurized fluid to lubricate the rollers 16a.
  • a thin layer of fluid for example a lubricating oil, can be particularly supplied and deposited both on the outer surface of the rollers 16a and on the inner surface 22a of the stator 20, via the rolling of the rollers 16a along the inner surface 22a.
  • the recess 21 of the stator 20 in which the rotor 10 is received is defined anteriorly and laterally by the stator case 25, and is closed at the rear by a plate 51.
  • the plate 51 is arranged transversely, in particular perpendicularly to the axis A1 of the stator 20 and the central axis A2 of the rotor 10.
  • the plate 51 is defined by a rear face 51b, shown in Figure 3a and facing the opposite side with respect to the rotor 10, and by a front face 51a, shown in Figure 3b and facing the rotor 10.
  • the plate 51 is defined by an outer edge having the same shape of the inner surface 22a that delimits the stator recess 21.
  • the plate 51 exerts a sealing action on the pressurized fluid contained within the stator case 25, so that any unwanted fluid releases are prevented.
  • the plate 51 is preferably made of a metal with high resistance to wear due to the fact that during operation of the machine 1 the plate 51 is facing the rotor 10 and all the components related thereto.
  • the plate 51 exhibits a central hole 53 for passage of the shaft 30.
  • the machine 1 is an engine, particularly an endothermic engine, during the operation of which, a fuel and comburent mixture in a gaseous state is present within the working volumes 40.
  • the pressurized fluid that circulates in the channels 19 is instead a lubricating oil, preferably a mineral and/or synthetic oil.
  • the machine 1 is so configured as to exhibit an n-vertices piston, namely the rotor 10, which is rotating eccentrically about the motor shaft, or the shaft 30, thereby generating working chambers 40 through its movement, inside of which chambers there are performed cyclically the four typical steps, i.e. the steps of suction - compression - combustion - and exhaust of the gasoline Otto cycle.
  • the plate 51, the rotor 10 and the stator case 25 are configured in order that a compensation between the pressures acting inside the machine 1 is achieved, so that the rotor 19 is axially balanced.
  • These components therefore define a balancing arrangement, owing to which the pressurized fluid is sent towards two opposite faces of the rotor 10, so that the rotor 10 is axially balanced.
  • the machine 1 comprises a feeding device for feeding the pressurized fluid previously mentioned, particularly oil, towards the rotor 10.
  • the feeding device may comprise an inlet conduit 54, which is afforded for example within a closing element 55 tightened against the stator case 25 in order to close the stator case 25, particularly via N threaded connection elements extending along respective axes A N shown in Figure 6 .
  • the closing element 55 is positioned in such a manner that the plate 51 comes to be interposed between the closing element 55 and the rotor 10. The latter is in turn interposed between the plate 51 and a transverse wall 26 of the stator case 25.
  • sealing elements 101 which are capable of exerting a static sealing action.
  • the pressurized fluid having a pressure equal to p1, is sent towards the rear face 51b of the plate 51 through the inlet conduit 54.
  • a balance channel 57 is formed, which penetrates through a thickness portion of the plate 51 and has a ring-closed plan shape extending about the axis A1 of the stator 20.
  • Two through holes 56 are facing the balance channel 57 through which holes, the pressurized fluid contained inside the balance channel 57 can reach the rotor 10.
  • the through holes 56 are arranged diametrically opposite to one another.
  • the balance channel 57 has a zone Ap, in plan view, indicated by a plurality of dots as illustrated in Figure 3a .
  • the pressurized fluid pressure p1 is acting on the zone Ap, which pressurized fluid is coming from the inlet conduit 54.
  • the front face 51a of the plate 51 is substantially smooth, i.e., free of any channel balancing.
  • two slots 52 can be identified into each of which slots 52, a through hole 56 is passing.
  • the slots 52 are arranged symmetrically with respect to an axis of the plate 51 which axis, in an operative configuration of the machine 1, coincides with the axis A1 of the stator 20.
  • the slots 52 are dimensioned in such a manner that at least one of them is steadily facing the channel 19, which channel 19 is formed on the rear face of the rotor 10 whatever the angular position of the rotor 10.
  • the pressurized fluid coming from the inlet conduit 54 and passing through the plate 51 can always flow through the rotor 10 in order to reach the front face thereof, i.e. the farthest face from the plate 51.
  • cavities 27 having, in plan view, the same shape of the slots 52 of the plate 51.
  • the cavities 27 are shaped as grooves, and are in mutual communication via a communication conduit which is formed within the stator casing 25 and is not shown.
  • a fluid with pressure p1 is present inside the cavities 27. This allows to balance the axial force due to the presence of fluid inside the slots 52 of the plate 51, which also has a pressure p1.
  • p1 - as previously already mentioned - signifies the fluid pressure acting on the rotor 10 by flowing through the plate 51, whilst Ar indicates the area, in plan view, of the channel 19, which channel 19 is afforded on the rear face of the rotor 10, shown with a plurality of dots in Figure 2 .
  • axial forces are further acting inside the stator 20, which arise during operation of the motor defined by the machine 1 due to the pressure generated in the working volumes 40 during the expansion and compression steps.
  • This forces balancing allows a hydrostatic floatability of the rotor 10 within the stator 20 during operation of the machine 1 as a motor.
  • Figure 6 illustrates diagrammatically how the forces are distributed which allow to obtain the balancing previously mentioned.
  • the machine 1 comprises a measuring and/or feedback system 60 which is configured for varying and adjusting the pressure p1, so that the condition previously mentioned is met.
  • Figure 4 shows schematically, by way of example, the measuring and/or feedback system 60, which comprises a pressure regulating valve 61, preferably with electronic control, for adjusting the pressure p1.
  • a pressure regulating valve 61 preferably with electronic control
  • Such pressure is preferably given by a mechanical pump connected with the machine 1 in the endothermic motor configuration.
  • p1 shall be selected such that the following condition is met: p 1 ⁇ Ap > pc ⁇ Ac + pe ⁇ Ae + p 1 ⁇ Ar
  • preloading elastic elements 100 shown in Figure 4 , which are capable of acting on the plate 51 with the machine 1 both at rest and in the operating configuration thereof.
  • the preloading elastic elements 100 may comprise cup springs or elastic elements of different kind, which are so configured as to exert a constant pressure on the plate 51 towards the inner portion of the machine 1, namely where the rotor 10 is housed.
  • the machine 1 can be shaped as a hydraulic motor, wherein the working fluid is a non-compressible fluid distributed within the working volumes 40, in particular an oil for mechanical transmissions.
  • machine 1 is shaped as a hydraulic motor, it may be convenient to not use an axial forces balancing system.
  • the stator 20 may comprise a pair of inlet openings 23a and a pair of outlet openings 23b, for example, arranged crosswise with respect to the axis A1 of the stator 20.
  • the machine 1 is configured as a pump, particularly a hydraulic pump wherein the working fluid is a non-compressible fluid distributed within the working volumes 40.
  • the examples shown so far include a rotor 10 provided with three vertices 11 defining an equilateral triangle, whereas the stator 20 is provided with two lobes 22.
  • the number of vertices 11 (and consequently the number of lobes 22) can be chosen arbitrarily.
  • Figure 5a there is shown a configuration in which the rotor is provided with four vertices 11 which define a square, while the stator comprises three lobes 22 distributed uniformly about the axis A1.
  • Figure 5b it is instead represented an example in which the rotor includes five vertices 11 defining a regular pentagon, while the stator comprises four lobes 22 separated by angles of 90°.
  • the invention has attained the preset aims.
  • stator is in contact only with the rolling elements placed within the vertices of the rotor, regardless of the number n of vertices of the rotor and the number (n-1) of the lobes of the stator. This allows to eliminate the apical segments of traditional Wankel engines, and at the same time to reduce friction and avoid the risk of jamming between rotor and stator.
  • the invention further allows to avoid coupling between the stator pinion and the rotor ring gear of the Wankel engine, which implies a considerable mechanical simplification and lightening, as well as a reduction of manufacturing costs in accordance with the present invention.
  • the radial sealing between rotor and stator is ensured by the auxiliary pressure p1 through which the rollers are pressed against the surfaces of the stator recess in a regular and constant manner.
  • the axial sealing is ensured by the hydrostatic balancing.
  • Figures 8 to 11 show a machine 101 according to an alternative embodiment, particularly a machine of the hydraulic type such as a hydraulic motor or hydraulic pump.
  • the machine 101 comprises a stator 120 exhibiting a recess 121 defined by an inner surface 122a.
  • the inner surface 122a is defined by a curve having the same equations previously mentioned.
  • Inside the stator 120 there is disposed a rotor 110, movable with a roto-orbital movement about the axis A1 of the recess 121.
  • the rotor 110 has a plurality of vertices, within each of which a rolling element 116 is mounted, which is suitable to roll on the inner surface 122a, so as to remain in constant contact with the inner surface 122a while the rotor 110 is roto-orbiting about the axis A1.
  • the rolling elements 116 are supported directly by the rotor 110 without any interposition by the sliding blocks.
  • n 3 vertices, however what is being disclosed hereinafter, generally applies to any integer and positive n value greater than or equal to 1.
  • a plurality of lobes or recesses 122 is defined Internally of the stator 120.
  • the number of lobes or recesses 122 of the stator 120 is equal to the number of vertices n of the rotor 110, reduced by one.
  • a plurality of chambers or working volumes 140 is defined, which are suitable for receiving a pressurized fluid or working fluid, e.g. oil.
  • the number of working volumes 140 is equal to 3. More generally, the number of working volumes 140 is equal to the vertices number n of the rotor 110.
  • a hole 112 is obtained inside the rotor 110, through which hole an eccentric portion 132 of a shaft 130 (see Figure 12 ) of the machine 101 is passing.
  • the shaft 130 extends along the axis A1, while the eccentric portion 132 is centered on the central axis A2.
  • the rotor 110 is so mounted as to freely rotate relative to the eccentric portion 132. In addition, the rotor 110 may freely slide axially with respect to the eccentric portion 132.
  • the recess 121 is formed internally of a stator case 125 shown in Figure 11 , which is ring-shaped in the example illustrated. This ring extends around the axis A1.
  • the stator case 125 is interposed between a first head or rear head 180, shown in Figure 9 , and between a second head or front head 181 shown in Figure 10 .
  • the rear head 180 and front head 181 respectively define a transverse wall and a further transverse wall defining the recess 121 transversely to the axis A1.
  • the rear head 180, the stator case 125 and the front head 181 are assembled in such a manner as to be stationary one to another.
  • the machine 101 shown in Figures 8 to 12 differs from the machine 1 disclosed above, basically due to the fact that the rotor 110 is balanced axially, i.e., it is balanced with respect to the forces acting thereon in a direction parallel to the central axis A2.
  • the rotor 110 is acting as a distributor element for distributing the pressurized fluid or working fluid within the working volumes 140, i.e. in order that the quantities and the time may be determined for the working fluid to respectively enter and exit from each working volume 140 at each revolution of the shaft 130 of the machine 101.
  • the machine 101 is provided with a plurality of passages or distribution openings 123, which allow the working fluid to respectively enter or exit from each working volume 140 along an axial direction, i.e. parallel to the axis A1. As shown in Figure 9 , the distribution openings 123 are afforded on the rear head 180.
  • the distribution openings 123 comprise a plurality of inlet openings 123a, through which the working fluid can enter the working volumes 140, and a plurality of outlet openings 123b, through which the working fluid can exit from the working volumes 140. As shown in Figure 8 , the inlet openings 123a and the outlet openings 123b are distributed alternatively around the axis A1.
  • the inlet openings 123a are acting as delivery openings.
  • the inlet openings 123a are acting as intake openings.
  • the distribution openings 123 are alternately opened and closed by the rotor 110 while the latter is rotating. In fact, during rotation of the rotor 110, the rotor is passing in front of each inlet opening 123, so that a certain time interval is defined during which each distribution opening 123 is thoroughly covered, i.e. closed, by the rotor 110. A further time interval may be defined during which each distribution opening 123 is left partially or completely uncovered by the rotor 110, so that the working fluid may cross this opening.
  • a distribution opening 123 is defined as inactive or passive during the time in which it is completely covered, i.e. closed by the rotor 110.
  • each distribution opening 123 will be defined as active during the time in which the rotor 110 is leaving that distribution opening 123 partially or completely uncovered.
  • N L 2 (n-1).
  • a machine 101 which is provided with 2 (n-1) openings, has n active openings and (n-2) passive openings in every instant of its operation.
  • a complete cycle of the machine 101 is carried out in a complete rotation of the shaft 130, namely in a 2 ⁇ rotation of the shaft 130 of the machine 101.
  • the reduction ratio between the shaft 130 and the rotor 110 is equal to 1/n, i.e., n revolutions of the shaft 130 are needed in order that the rotor 110 makes a complete revolution on itself. Consequently, a machine cycle 101 corresponds to an R R rotation of the rotor 110 equal to 2 ⁇ / n.
  • a P A activity period may be defined, i.e. a rotation angle of the rotor 110 in which the distribution opening 123 is active for each revolution of the shaft 130.
  • a P P passivity period can be defined, i.e. a rotation angle of the rotor 110 in which the distribution opening 123 is inactive for each revolution of the shaft 130.
  • the P A activity period is the same for all distribution openings 123.
  • each distribution opening 123 remains active for the time necessary for the rotor 110 to perform a 90° rotation, whilst it is passive for the time necessary for the rotor 110 to perform a 30° rotation.
  • n 4
  • each distribution opening 123 is completely obscured, that is covered, by the rotor 110. This means that the pressure of the working fluid existing within the distribution opening 123 generates a force which is directed in the axial direction (i.e. parallel to the axis A1), which force is entirely applied to the rotor 110. It follows that the rotor 110 is axially unbalanced, i.e. it is subject to axial forces the resultant of which differs from zero.
  • each distribution opening 123 may be partially obscured, i.e. covered by the rotor 110. This helps to axially unbalance the rotor 110, since the working fluid present within the obscured portion of the distribution opening 123 exerts a direct force on the rotor 110 which direct force is parallel to the axis A1.
  • the rotor 110 (as well as the rotor 10 of Figures 1 to 7 ) has a dual function. Firstly, the rotor 110 is acting as an expansion/compression organ, i.e. it determines the volume change of the working volumes or chambers 140, similarly to a piston of a reciprocating machine. Secondly, the rotor 110 is acting as a distributor element, that is, it allows the working fluid to be distributed within each chamber 140.
  • an active inlet or delivery opening 123a is associated to this chamber 140 when an expansion step is occurring within the chamber 140, so that the working fluid is allowed to enter the chamber 140 in question. If instead, a contraction step is occurring within a chamber 140, to that chamber 140 an active outlet opening 123b is associated so that the working fluid is allowed to exit the chamber 140.
  • a distribution opening 123 is passive, that opening is isolated from all 140 chambers.
  • the machine 101 is a pump, when the volume of a chamber 140 is increasing, to that chamber 140 an active inlet or intake opening 123a is associated, so that the working fluid is allowed to enter the chamber 140 in question. If instead the volume of a chamber 140 is decreasing, to that chamber 140 an active delivery opening 123b is associated, so that the working fluid is allowed to exit the chamber 140.
  • a distribution opening 123 is passive, that opening is isolated from all 140 chambers.
  • a plurality of balancing recesses 175 - i.e. non-through cavities - is obtained, which are arranged in a position facing to the distribution openings 123.
  • the number of balancing recesses 175 corresponds to the number of distribution openings 123, namely it is equal to 2 (n-1).
  • Each balancing recess 175 is disposed in an axially opposite position with respect to a corresponding distribution opening 123. In other words, each balancing recess 175 is aligned with the corresponding distribution opening 123 along a direction parallel to the axis A1.
  • each balancing recess 175 is equal to the shape in plan of the corresponding distribution opening 123.
  • each balancing recess 175 has the same dimensions of the corresponding distribution opening 123.
  • Each balancing recess 175 is in fluid communication with the corresponding distribution opening 123.
  • each distribution opening 123 is in fluid communication with a transverse conduit 176, which extends transversely to the rear head 180, in particular perpendicularly to the axis A1.
  • Each transverse conduit 176 is in fluid communication with a longitudinal conduit 177, which extends parallel to the axis A1 by passing through the stator case 125.
  • Each longitudinal conduit 177 is in fluid communication with a further transverse conduit 178 which is formed within the thickness of the front head 181 and directed transversely, in particular perpendicularly, to the axis A1.
  • Each additional transverse conduit 178 is flowing in turn into a balancing recess 175.
  • each balancing recess 175 By placing each balancing recess 175 in fluid communication with the corresponding distribution opening 123, it is ensured that in each balancing recess 175 the same working fluid is present, and thus the same pressure, which pressure is present in the corresponding distribution opening 123. Since each balancing recess 175 is axially opposite to the corresponding distribution opening 123, as well dimensioned such as that distribution opening, when the rotor 110 is closing a distribution opening 123 completely or partially, the corresponding balancing recess 175 is closed with the same closing level of the distribution opening 123.
  • the working fluid present within a balancing recess 175 therefore exerts, on a face of the rotor 110, a force which is equal and opposite to the force that the working fluid, present in the corresponding distribution opening 123, is exerting on a further face of the rotor 110. In this way, the rotor 110 is axially balanced.
  • the face and the further face of the rotor 110 mentioned above are opposite one to another and arranged transversely, in particular perpendicularly, to the axis A1.
  • the distribution openings 123 may be placed in fluid communication with the corresponding balancing recesses 175 via conduits formed within the rotor 110 rather than within the stator case 125.
  • the distribution openings 123, the transverse conduits 176, the longitudinal conduits 177, the additional transverse conduits 178 and balancing recesses define, within the machine 101, a balancing arrangement which allows the pressurized fluid to be sent on two opposite faces of the rotor 110, said opposite faces being arranged transversely to the axis A1. In this way, the pressurized fluid is exerting equal and opposite axial forces on the opposite faces of the rotor 110 so that the rotor 110 results balanced in the axial direction.
  • the rotor is axially balanced by means of hydraulic forces, i.e. by means of forces exerted by a pressurized fluid on two opposite faces of the rotor.
  • the rotor appears in a floating condition within the stator, in that the rotor, inside the stator, is surrounded by a fluid, which fluid is exerting equal and opposite forces on axially opposite faces of the rotor. This allows to axially balance the rotor in a particularly simple and effective manner.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Connection Of Motors, Electrical Generators, Mechanical Devices, And The Like (AREA)
  • Rotary Pumps (AREA)

Claims (15)

  1. Maschine (1; 101), umfassend:
    - einen Rotor (10; 110) mit einer voreingestellten Anzahl (n) von Endbereichen (11);
    - einen Stator (20; 120), der eine Vertiefung (21; 121) aufweist, die durch eine Innenfläche (22a; 122a) begrenzt ist, wobei der Rotor (10; 110) exzentrisch im Inneren der Vertiefung (21; 121) untergebracht ist und im Verhältnis zum Stator (20; 120) in einer drehenden Kreisbewegung um eine Achse (A1) der Vertiefung (21; 121) bewegbar ist;
    - eine Welle (30; 130) mit einem exzentrischen Abschnitt (32; 132), wobei der Rotor (10; 110) mit einem Loch (12; 112) versehen ist, mit dem der exzentrische Abschnitt (32; 132) in Eingriff steht, wobei der Rotor (10; 110) derart installiert ist, dass er sich in Bezug auf den exzentrischen Abschnitt (32; 132) der Welle (30; 130) frei drehen kann,
    wobei jeder Endbereich (11) des Rotors (10; 110) mit einem Rollelement (16; 116) versehen ist, das zum Rollen auf der Innenfläche (22a; 122a) geeignet ist, sodass es mit der Innenfläche (22a; 122a) in Kontakt bleibt, während der Rotor (10; 110) drehend um die Achse (A1) kreist, wobei der Rotor quer zu der Achse (A1) durch eine Fläche und durch eine weitere Fläche begrenzt ist, die einander gegenüberliegen, dadurch gekennzeichnet, dass
    die Innenfläche (22a; 122a) der Vertiefung (21; 121) in einer kartesischen Ebene senkrecht zur Achse (A1) durch eine Kurve definiert ist, der ein im Voraus festgelegter Punkt, wenn ein Rollumfang an einem Basisumfang rollt, außerhalb des Basisumfangs folgt, wobei die Kurve die folgenden Gleichungen aufweist: x = n − 1 R + R cos α − Ecos nα ± Rr cosarctg n − 1 R + R sin α − nEsin nα n − 1 R + R cos α − nEcos nα
    Figure imgb0044
     und y = n − 1 R + R sin α − Esin nα ± Rr sinarctg n − 1 R + R sin α − nEsin nα n − 1 R + R cos α − nEcos nα
    Figure imgb0045
     wobei:
    - n eine Ganzzahl größer oder gleich eins gleich der Anzahl der Endbereiche (11) des Rotors (10, 110) ist;
    - (n-1) R der Radius des Basisumfangs ist;
    - R der Radius des Rollumfangs ist;
    - Rr der Radius jedes Rollelements (16) ist;
    - α ein Winkel ist, der eine Winkelposition des Rollumfangs in Bezug auf den Basisumfang angibt, die mit der Winkelposition des Rotors (10; 110) um die Achse (A1) der Vertiefung (21; 121) übereinstimmt;
    - E der Abstand des im Voraus festgelegten Punkts von der Mitte des Rollumfangs gemessen an einem Segment ist, das die Mitte des Rollumfangs mit der Mitte des Basisumfangs verbindet, wenn der Winkel (a) gleich null ist, wobei der Abstand (E) ferner die Exzentrizität zwischen dem Rotor (10; 110) und dem Stator (20; 120) ausdrückt,
    wobei der Rotor (10; 110) so installiert ist, dass er in Bezug auf den exzentrischen Abschnitt (32; 132) der Welle (30; 130) frei axial gleiten kann, wobei die Maschine (1;101) mit einer Ausgleichsanordnung versehen ist, die dazu konfiguriert ist, ein Druckfluid an die Fläche und an die weitere Fläche zu leiten, sodass das Druckfluid axial ausgeglichene Kräfte auf den Rotor (10; 110) ausübt.
  2. Maschine nach Anspruch 1, und ferner umfassend eine Vielzahl von Öffnungen (23a, 23b; 123) zum Einleiten des Druckfluids zwischen den Rotor (10; 110) und den Stator (20; 120) und zum Ablassen des Druckfluids aus der Maschine (1;101) heraus.
  3. Maschine nach Anspruch 2, wobei die Öffnungen (23a, 23b; 123) der Vielzahl an einer Querwand (26; 180) gebildet sind, die im Verhältnis zu der Vertiefung (21; 121) fixiert ist und quer zur Achse (A1) angeordnet ist, sodass das Druckfluid in einer Richtung parallel zur Achse (A1) zum Rotor (10; 110) oder aus der Maschine (1; 101) strömt.
  4. Maschine nach Anspruch 3, und ferner umfassend eine weitere Querwand (181), die sich quer zur Achse (A1) erstreckt, wobei eine Vielzahl von Ausgleichsvertiefungen (175) an der Querwand (181) erlangt wird, wobei jede Ausgleichsvertiefung (175) mit einer jeweiligen Öffnung (123) der Vielzahl von Öffnungen in Fluidverbindung steht.
  5. Maschine nach Anspruch 4, wobei jede Ausgleichsvertiefung (175) der Vielzahl von Vertiefungen in einer Richtung parallel zur Achse (A1) an der jeweiligen Öffnung (123) der Vielzahl von Öffnungen ausgerichtet ist, wobei die Ausgleichsvertiefung (175) eine Form und Abmessungen aufweist, die der Form und den Abmessungen der jeweiligen Öffnung (123) entsprechen.
  6. Maschine nach Anspruch 4 oder 5, wobei die weitere Fläche des Rotors (110) der Querwand (180) zugewandt ist, wobei die Fläche des Rotors (110) der weiteren Querwand (181) zugewandt ist.
  7. Maschine nach einem der Ansprüche 2 bis 6, wobei die Anzahl von Öffnungen (123) der Vielzahl gleich 2(n-1) ist.
  8. Maschine nach einem der vorangehenden Ansprüche, die als ein Hydraulikmotor oder eine Hydraulikpumpe konfiguriert ist.
  9. Maschine nach Anspruch 2 oder 3, wobei die Anzahl von Öffnungen (23a; 23b) der Vielzahl gleich (n-1) ist, wobei die Maschine vorzugsweise als ein endothermer Motor konfiguriert ist.
  10. Maschine nach Anspruch 1, und ferner umfassend eine Vielzahl von Gleitblöcken (16b), von denen jeder wenigstens teilweise in einem Sitz (17) untergebracht ist, der in einem Endbereich (11) des Rotors (10) gebildet ist, wobei jeder Gleitblock (16b) ein Rollelement (16) trägt, sodass das Rollelement (16) sich in Bezug auf den entsprechenden Gleitblock (16b) frei drehen kann.
  11. Maschine nach Anspruch 10 und ferner umfassend eine Zuführvorrichtung zum Zuführen des Druckfluids zwischen den Rotor (10) und den Stator (20), sodass das Druckfluid die Gleitblöcke (16b) zum Stator (20) schiebt, wodurch die Rollelemente (16) an die Innenfläche (22a) der Vertiefung (21) angedrückt bleiben.
  12. Maschine nach Anspruch 11, wobei an der Fläche und der weiteren Fläche des Rotors (10) jeweilige Kanäle (19) gebildet sind, die zum Aufnehmen des Druckfluids geeignet sind, wobei jeder Kanal so angeglichen ist, dass er die Endbereiche (11) des Rotors (10) miteinander in Fluidverbindung setzt, wobei der Kanal (19), der an der Fläche des Rotors (10) gebildet ist, vorzugsweise symmetrisch in Bezug auf den Kanal (19) ist, der an der weiteren Fläche des Rotors (10) gebildet ist.
  13. Maschine nach Anspruch 12, wobei der Kanal (19), der an der Fläche des Rotors (10) gebildet ist, mit dem Kanal (19), der an der weiteren Fläche des Rotors (10) gebildet ist, durch eine Nut (16f) in Verbindung steht, die an der Grenzfläche zwischen einem Gleitblock (16b) und seinem entsprechenden Sitz (17) erlangt wird, sodass das Druckfluid, das in der Nut (16f) strömt, den jeweiligen Gleitblock (16b) gegen die Innenfläche (22a) der Vertiefung (21) drückt, und wobei vorzugsweise jeder Gleitblock (16b) wenigstens ein Schmierloch (16e) aufweist, damit Druckfluid, das in der entsprechenden Nut (16f) strömt, das Rollelement (16) erreicht, das von dem Gleitblock (16b) getragen wird, sodass das Rollelement (16) geschmiert werden kann.
  14. Maschine nach einem der Ansprüche 11 bis 13, wobei die Maschine als eine endothermer Motor angeglichen ist, wobei die Zuführvorrichtung mit einem Messungs- und Rückkopplungssystem (60) zum Steuern des Drucks des Druckfluids assoziiert ist, derart, dass axial ausgeglichene Kräfte auf den Rotor (10) einwirken, und wobei der Rotor (10) vorzugsweise zwischen einer Querwand (26) des Stators und einer Ausgleichsplatte (51) an einer Fläche (51b) der Ausgleichsplatte (51) angeordnet ist, an der ein Ausgleichskanal (57) gebildet ist, wobei der Ausgleichskanal (57) geeignet ist, um das Druckfluid von der Zuführvorrichtung aufzunehmen, wobei der Ausgleichskanal (57) und Kanäle (19), die an dem Rotor (10) gebildet sind, jeweilige Flächen (Ar, Ap) in Draufsicht aufweisen, die so abgemessen sind, dass Druckfluid, das auf die Flächen (Ar, Ap) einwirkt, in der Vertiefung (21) axiale Kräfte erzeugt, die die weiteren axialen Kräfte aufgrund von Drücken ausgleichen können, die während der Kompressions- und Expansionsschritte des endothermen Motors erzeugt werden
  15. Maschine nach einem der vorangehenden Ansprüche, wobei:
    die im Voraus festgelegte Anzahl (n) der Endbereiche (11) des Rotors (10; 110) eine Ganzzahl größer als oder gleich drei ist;
    die Endbereiche (11) des Rotors (10; 110) entsprechende Eckpunkte eines regelmäßigen Vielecks definieren;
    die Vertiefung (21; 121) des Stators (20; 120) eine Vielzahl von Flügeln (22; 122) aufweist, die eine Anzahl von Flügeln (22; 122) gleich der im Voraus festgelegten Anzahl (n) von Endbereichen des Rotors (10; 110) reduziert um eins umfasst,
    und wobei vorzugsweise jedes Rollelement (16; 116) eine Rolle (16a) mit einer jeweiligen Achse ist, die an einem Eckpunkt des regelmäßigen Vielecks angeordnet ist.
EP16716277.5A 2015-02-12 2016-02-11 Antriebs-oder arbeitsmaschine mit ausgleichsanordnung Active EP3256695B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
ITMO20150026 2015-02-12
PCT/IB2016/050730 WO2016128926A1 (en) 2015-02-12 2016-02-11 Driving or operating machine with balancing arrangement

Publications (2)

Publication Number Publication Date
EP3256695A1 EP3256695A1 (de) 2017-12-20
EP3256695B1 true EP3256695B1 (de) 2021-04-21

Family

ID=52597120

Family Applications (1)

Application Number Title Priority Date Filing Date
EP16716277.5A Active EP3256695B1 (de) 2015-02-12 2016-02-11 Antriebs-oder arbeitsmaschine mit ausgleichsanordnung

Country Status (2)

Country Link
EP (1) EP3256695B1 (de)
WO (1) WO2016128926A1 (de)

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB583035A (en) * 1943-08-20 1946-12-05 Bernard Maillard A rotary machine generating variable volumes
US3999905A (en) * 1975-11-17 1976-12-28 Caterpillar Tractor Co. Rotary mechanism
US4072449A (en) * 1976-03-12 1978-02-07 Caterpillar Tractor Co. Combined seal biasing spring and check valve for rotary mechanisms
AT380636B (de) * 1983-02-16 1986-06-25 Walter Mag Schwab Rotationspumpe zur verwendung als blut- und herzpumpe
DE3519186A1 (de) * 1984-12-24 1986-12-04 Josef 5000 Köln Pappert Verbesserung am kreiskolbenmotor (wankelmotor)
DE3508072A1 (de) * 1985-03-07 1986-09-18 Dieter 3380 Goslar Brox Planetenverdichter
US5391067A (en) * 1993-07-20 1995-02-21 Saunders; James E. Rotary fluid displacement device
JP2013521433A (ja) * 2010-03-01 2013-06-10 ブライト エナジー ストレージ テクノロジーズ，エルエルピー． 回転式圧縮機−膨張機システムならびに関連する使用および製造方法
US9121405B2 (en) * 2012-11-12 2015-09-01 Ge Oil & Gas Compression Systems, Llc Trochoidal rotary device

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

Also Published As

Publication number Publication date
EP3256695A1 (de) 2017-12-20
WO2016128926A1 (en) 2016-08-18

Similar Documents

Publication Publication Date Title
EP1711686B1 (de) Drehmechanismus
RU2343290C2 (ru) Роторный двигатель внутреннего сгорания
JP2009517583A (ja) 内燃機関
US904974A (en) Internal-combustion rotary engine.
US7080976B2 (en) Volumetric rotary machine
EP3256695B1 (de) Antriebs-oder arbeitsmaschine mit ausgleichsanordnung
WO2021232025A1 (en) Rotary machine with hub driven transmission articulating a four bar linkage
JPH057524B2 (de)
US4373484A (en) Rotary piston mechanism
AU2001282621B2 (en) Rotary fluid machinery
CA2857737C (en) Rotary internal combustion engine with static oil seal
KR100196766B1 (ko) 로터형 펌프
US4021160A (en) Orbital motor
KR100395080B1 (ko) 로터리내연엔진
WO1998059160A1 (en) Axial piston rotary machine
US4051819A (en) Rotary block engine
US3915599A (en) Structure for preventing leakage of lubricating oil in rotary-piston internal combustion engines
RU2078225C1 (ru) Роторно-поршневой двигатель внутреннего сгорания
RU2075616C1 (ru) Роторно-поршневой двигатель внутреннего сгорания (варианты)
RU2107830C1 (ru) Кривошипно-маятниковый роторный двигатель ванькова
AU2004269045B2 (en) Rotary mechanism
WO1984003124A1 (en) Rotary piston mechanism
RU2072433C1 (ru) Роторно-поршневой двигатель внутреннего сгорания
RU2091596C1 (ru) Роторно-поршневой двигатель внутреннего сгорания
RU2505690C2 (ru) Роторно-поршневой двигатель внутреннего сгорания

Legal Events

Date Code Title Description
STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE INTERNATIONAL PUBLICATION HAS BEEN MADE

PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: REQUEST FOR EXAMINATION WAS MADE

17P Request for examination filed

Effective date: 20170908

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

AX Request for extension of the european patent

Extension state: BA ME

DAV Request for validation of the european patent (deleted)
DAX Request for extension of the european patent (deleted)
GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: GRANT OF PATENT IS INTENDED

INTG Intention to grant announced

Effective date: 20200605

GRAJ Information related to disapproval of communication of intention to grant by the applicant or resumption of examination proceedings by the epo deleted

Free format text: ORIGINAL CODE: EPIDOSDIGR1

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: REQUEST FOR EXAMINATION WAS MADE

INTC Intention to grant announced (deleted)
GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: GRANT OF PATENT IS INTENDED

INTG Intention to grant announced

Effective date: 20201118

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE PATENT HAS BEEN GRANTED

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 602016056440

Country of ref document: DE

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

REG Reference to a national code

Ref country code: AT

Ref legal event code: REF

Ref document number: 1384822

Country of ref document: AT

Kind code of ref document: T

Effective date: 20210515

REG Reference to a national code

Ref country code: LT

Ref legal event code: MG9D

REG Reference to a national code

Ref country code: AT

Ref legal event code: MK05

Ref document number: 1384822

Country of ref document: AT

Kind code of ref document: T

Effective date: 20210421

REG Reference to a national code

Ref country code: NL

Ref legal event code: MP

Effective date: 20210421

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210421

Ref country code: LT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210421

Ref country code: NL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210421

Ref country code: HR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210421

Ref country code: AT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210421

Ref country code: BG

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210721

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: PL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210421

Ref country code: PT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210823

Ref country code: NO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210721

Ref country code: RS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210421

Ref country code: SE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210421

Ref country code: LV

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210421

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210722

Ref country code: IS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210821

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 602016056440

Country of ref document: DE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210421

Ref country code: SM

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210421

Ref country code: CZ

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210421

Ref country code: DK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210421

Ref country code: EE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210421

Ref country code: RO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210421

Ref country code: ES

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210421

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed

Effective date: 20220124

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210821

Ref country code: AL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210421

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MC

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210421

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

REG Reference to a national code

Ref country code: BE

Ref legal event code: MM

Effective date: 20220228

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LU

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20220211

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20220228

Ref country code: CH

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20220228

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: BE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20220228

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: HU

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT; INVALID AB INITIO

Effective date: 20160211

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: IE

Payment date: 20240220

Year of fee payment: 9

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210421

Ref country code: CY

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210421

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20240228

Year of fee payment: 9

Ref country code: GB

Payment date: 20240220

Year of fee payment: 9

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: IT

Payment date: 20240212

Year of fee payment: 9

Ref country code: FR

Payment date: 20240226

Year of fee payment: 9

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210421