WO2013160835A1 - Machine volumétrique tournante à pistons radiaux - Google Patents

Machine volumétrique tournante à pistons radiaux Download PDF

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Publication number
WO2013160835A1
WO2013160835A1 PCT/IB2013/053212 IB2013053212W WO2013160835A1 WO 2013160835 A1 WO2013160835 A1 WO 2013160835A1 IB 2013053212 W IB2013053212 W IB 2013053212W WO 2013160835 A1 WO2013160835 A1 WO 2013160835A1
Authority
WO
WIPO (PCT)
Prior art keywords
relative
fact
machine
inner ring
revolving
Prior art date
Application number
PCT/IB2013/053212
Other languages
English (en)
Inventor
Davide Pecorari
Original Assignee
Ecotech Industrial S.R.L.
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 Ecotech Industrial S.R.L. filed Critical Ecotech Industrial S.R.L.
Priority to EP13727991.5A priority Critical patent/EP2859219A1/fr
Publication of WO2013160835A1 publication Critical patent/WO2013160835A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
    • F03C1/00—Reciprocating-piston liquid engines
    • F03C1/02—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders
    • F03C1/04—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinders in star or fan arrangement
    • F03C1/0403—Details, component parts specially adapted of such engines
    • F03C1/0428—Supporting and guiding means for the pistons
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
    • F03C1/00—Reciprocating-piston liquid engines
    • F03C1/02—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders
    • F03C1/04—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinders in star or fan arrangement
    • F03C1/0403—Details, component parts specially adapted of such engines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
    • F03C1/00—Reciprocating-piston liquid engines
    • F03C1/02—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders
    • F03C1/04—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinders in star or fan arrangement
    • F03C1/0403—Details, component parts specially adapted of such engines
    • F03C1/0419—Arrangements for pressing or connecting the pistons against the actuated cam
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/0404—Details or component parts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/0404—Details or component parts
    • F04B1/0426—Arrangements for pressing the pistons against the actuated cam; Arrangements for connecting the pistons to the actuated cam
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/0404—Details or component parts
    • F04B1/0439—Supporting or guiding means for the pistons

Definitions

  • the present invention relates to a rotating volumetric machine with radial pistons.
  • the rotating volumetric machine with radial pistons to which this invention relates can work both as a pump and an engine, such as an internal combustion engine.
  • Known rotating volumetric machines generally comprise:
  • a central distributor that defines at least one supplying channel and a discharge channel for the working fluid
  • a rotor element mobile in rotation around a first axis and with a plurality of radial chambers communicating with at least one between the supplying channel and discharge channel and in which the relative pistons are housed mobile along a sliding direction;
  • a contrast device against the radial thrust of the pistons which comprise at least one fixed outer ring and one inner ring mobile in rotation with respect to the external ring around a second rotational axis eccentric to the first axis, the inner ring being fixed to the pistons along their sliding direction;
  • WO 03060321 describes a rotating volumetric machine in which the pistons are associated to the inner ring by means of a dovetail type connection that allows the shift of the pistons themselves along a direction that is perpendicular to the sliding direction. The movement of the pistons along the relative sliding directions causes the rotation of the inner ring around the second axis.
  • the joint connecting in rotation the inner ring to the rotor element is fitted with four seats staggered by 90° from each other, in which the respective protrusions are fitted sliding.
  • a pair of protrusions is arranged, of which a first pair of protrusions integral to the inner ring and a second pair of protrusions integral to the rotor element.
  • the protrusions slide inside the relative seats defined on the joint, which therefore moves in an alternate rotary- translational motion.
  • the working tolerances play a fundamentally important role in order to ensure their correct operation. More specifically, the clearance between the protrusions and the relative seats must be sufficiently small to avoid, during motion transmission, mutual misalignment and consequently high peak pressures between the parts in contact, which in some cases may even lead to breakage. Moreover, the greater the clearance between the protrusions and relative seats, the greater the noise of the volumetric machine. At the same time there must be sufficient clearance to allow the correct movement of the mutually moving parts. It thus follows that the working tolerances must be very close and carefully assessed to allow on one hand the correct operation of the volumetric machine and on the other hand avoid unwanted breakages and vibrations. This requires special attention during the design and production phases, which translates into long production times and higher costs.
  • Another drawback lies in the fact that the surfaces of mutually moving parts may weld, particularly in the case of micro-shifts of the protrusions inside the relative seats due to minor axial misalignments.
  • the forced direction of movement of the piston with respect to the inner ring defined by the dovetail connection may lead to the formation of "hot" areas in which the lubricant film between the mutually moving parts disappears, with the consequent risk of seizure.
  • the main aim of the present invention is to provide a rotating volumetric machine with radial pistons which, compared to known rotating volumetric machines, drastically reduces the loss of energy due to the friction that occurs during the motion transmission from the inner ring to the rotor element.
  • one object of this invention is to provide a rotating volumetric machine with radial pistons which during use maintains a practically constant oil film between the mutually moving parts which transfer the motion from the inner ring to the rotor element.
  • One object of this invention is, compared to the known machines, to drastically reduce the influence of the working tolerances on the correct operation of the machine itself. More specifically, one object of this invention is to provide a rotating volumetric machine with radial pistons which can be designed and manufactured with less strict working tolerances than those of known machines, without negatively affecting performance, at the same time reducing production times and costs.
  • Another object of this invention is to provide a machine that is drastically less noisy than those of known type.
  • Another object of this invention is to provide a rotating machine with radial pistons which can be designed for breakage rather than for deformation, i.e. that is able to operate correctly even in the presence of slight deformations of the mutually moving parts.
  • Yet another object of this invention is to avoid unwanted welds between the mutually moving parts.
  • This invention also aims to improve the hydraulic balancing of the piston and maintain correct lubrication between the pistons and the inner ring, in order to reduce as far as possible the risk of seizure.
  • Another object of the present invention is to provide a rotating volumetric machine with radial pistons which allows to overcome the mentioned drawbacks of the state of the art in the ambit of a simple, rational, easy and effective to use as well as low cost solution.
  • Figure 1 is a longimdinal section view of a volumetric machine according to the invention.
  • Figure 2 is a section view along the track plane II-II in figure 1 ;
  • Figure 3 is a section view of the fastening means of the machine in figure 1;
  • Figure 4 is an axonometric yiew of the machine in figure 1;
  • Figure 5 is a plan view of the correcting joint of the machine in figure 4.
  • Figure 6 is a plan view of a connecting joint in an embodiment alternative to that in figure 5;
  • Figure 7 is a section view of the coupling between a rotating element and the relative seat.
  • a rotating volumetric machine with radial pistons.
  • the machine 1 can work both as a pump and an engine.
  • the machine 1 comprises a bearing structure 2, 3 comprising a first and second element 2 and 3 hollow inside and mutually coupled using screwing means which are not represented in the figures.
  • the bearing structure 2, 3 defines a chamber in which a distributor 4 of a working fluid is housed, such as gas, air, water, oil, etc...
  • the distributor 4 comprises at least a supplying channel 5 and at least a discharge channel 6 of the working fluid.
  • the supplying channel 5 comprises a cut 5a connected to a supplying device of the working fluid (not visible in detail in the figures) and two breakings 5b, 5c communicating with the cut 5a by means of two pipes 5d, 5e through which the working fluid flows.
  • the breakings 5b, 5c are communicating with each other and between them is a relative strengthening ribbing.
  • the discharge channel 6 comprises a cut 6a connected to a discharge device of the working fluid (not visible in detail in the figures), and two breakings 6b, 6c communicating with the cut 6a by means of two pipes 6d, 6e through which the working fluid flows.
  • the breakings 6b, 6c are communicating with each other and between them is a relative strengthening ribbing.
  • the distributor 4 has a longitudinal symmetry axis and is floating inside the chamber defined by the elements 2 and 3. More specifically, the distributor 4 is angularly mobile to vary the timing of the machine 1 , as will be explained in more detail below. The angular rotation of the distributor 4 is done by means that are not shown in the figures. Moreover, given that, as said, the machine 1 can work both as a pump and as an engine, the distributor 4 is also axially mobile.
  • La machine 1 then comprises at least one rotor element 7 arranged around the distributor 4 and mobile in rotation around a first axis 8.
  • the first axis 8 of rotation of the rotor element 7 coincides substantially with the longitudinal symmetry axis of the distributor 4 which, on the other hand, is locked in rotation.
  • first rolling means 9,10 composed, e.g., by a first and second bearing 9 and 10.
  • the bearings 9 and 10 maintain the coaxial position between the distributor 4 and the rotor element 7.
  • second rolling means 19,20 composed, e.g., by a tliird and fourth bearing 19 and 20.
  • the rotor element 7 comprises a plurality of radial chambers 11 , each of which is in coimnunication with at least one between the pipes 5 and 6 and more specifically with one of the breakings 5b, 5c, 6b, 6c. As the rotor element 7 rotates around the first axis 8, each chamber 11 is placed in hydraulic communication, in sequence, with each of the breakings 5b, 5c, 6b, 6c.
  • the sliding direction 13 coincides substantially with the symmetry axis of the relative chamber 11.
  • the machine 1 comprises, then, at least one contrast device 14 against the radial thrust of the pistons 12.
  • the contrast device 14 comprises at least an outer ring 15 and at least an inner ring 16 arranged around the rotor element 7.
  • the inner ring 16 is mobile in rotation with respect to the outer ring 15 around a second axis 17 of rotation substantially parallel and misaligned with respect to the first axis 8, as can be seen in figure 1.
  • the outer ring 15 is fixed and integrally associated with the first element 2 and between the outer ring itself and the inner ring 16 are positioned rolling means 18 such as, e.g., one or more series of cylindrical rollers.
  • rolling means 18 such as, e.g., one or more series of cylindrical rollers.
  • the assembly made up of the outer ring 15, rolling means 18 and inner ring 16 thus defines an integrated bearing, on which rolling tracks are made in the elements of the machine 1 itself.
  • the second axis 17 of rotation of the inner ring 16 coincides substantially with the symmetry axis of the outer ring 15 which, as stated above, is offset with respect to the first axis 8 of rotation of the rotor element 7.
  • the misalignment of the axes 8 and 17 defines the displacement of the machine 1.
  • the machine 1 comprises adjusting means of the position of the second axis 17, not shown in the figures, which therefore adjust also the eccentricity with respect to the first axis 8.
  • the displacement of machine 1 is consequently modified which is therefore of variable displacement type.
  • the contrast device 14 comprises fastening means 21 which fix each piston to the inner ring 16 along the relative sliding direction 13 and allow the shift along at least a further transversal direction to the sliding direction itself.
  • the fastening means 21 comprise, for each piston 12, at least a first locator element 22 and a second locator element 24 integrally associated with the inner ring 16.
  • the first and second locator elements 22 and 24 define a first and a second locator surface 22 a and 24a respectively, facing one another and arranged transversally with respect to the sliding direction 13 of the piston
  • each piston 12 is suitable for cooperating with the first locator surface 22a by means of its head 12a and with the second locator surface 24a by means of a contact surface 12b.
  • the locator surfaces 22a and 24a are arranged perpendicularly to the sliding direction 13 of the relative piston 12.
  • the second locator element 24 is fitted inside the relative piston 12 through a through opening defined in it.
  • each second locator element 24 has a stem fitted through the relative piston 12 and associated integrally to the inner ring 16 at one end and has, on the opposite end of the stem with respect to the inner ring 16, a head which defines the second locator surface 24a.
  • the stem defines a lateral surface 24b which extends substantially parallel to the sliding direction 13 of the relative piston 12.
  • the stem of the second locator element 24 has a substantially circular section, which can be constant or variable along the longitudinal extension thereof.
  • the fastening means 21 can have various embodiments, the figures enclosed represent only one of these.
  • the fastening means 21 comprise at least one slot defined in each piston 12 and extending along the further shift direction of the pistons themselves.
  • the relative second locator element 24 is fitted inside a corresponding slot and each piston 12 is mobile with respect to the relative second locator element itself along the direction defined by the slot itself.
  • each piston 12 rests with its head 12a against the first locator surface 22a.
  • the guide plane is defined by at least one of the locator surfaces 22a, 24a.
  • the fastening means 21 comprise at least an intermediate element placed between each piston 12 and the relative second locator surface 24a and on which at least one elongated slot is defined.
  • the relative second locator element 24 is fitted inside the slot and the intermediate element is mobile in rotation around the second locator element itself. More specifically, the intermediate element is placed between the inner walls 12c of the relative piston 12 and is released in rotation with respect to it; each piston 12 therefore moves with respect to the second locator element 24 along the direction defined each time by the orientation of the slot obtained on the intermediate element.
  • each piston 12 are spaced apart from the lateral surface 24b of the relative second locator element 24 and the fastening means 21 comprise at least one intermediate element 32,33 Fitted on the relative second locator element 24 and placed between the second locator surface 24a and a contact surface 12b defined in correspondence to the inner wall 12c of the corresponding piston 12.
  • This intermediate element 32, 33 is mobile both with respect to the second locator element 24 and the piston 12, supporting the latter during its shift along the relative guide plane.
  • the intermediate element 32,33 is therefore contained between the inner walls 12c of the relative piston, where the distance between two areas of the inner side walls 12c arranged on opposite sides of the relative second locator element 24 is greater than the diameter of the latter, obviously in the case in which it has a substantially circular section.
  • the fastening means 21 comprise at least two intermediate elements 32, 33, of which a first intermediate element 32 and a second intermediate element 33 released to one another, placed between each piston 12 and the relative second locator element 24.
  • the first intermediate element 32 rests against the second locator surface 24a and the second intermediate element 33 rests on one side against the first intermediate element 32 and on the other against the contact surface 12b.
  • the intermediate elements 32, 33 are mobile with respect to the relative second locator element 24, their internal diameter being greater than the external diameter of the relative lateral surface 24b, and with respect to the relative piston 12. More specifically, the intermediate elements 32 and 33 have a substantially circular section and their external diameters are less than the internal diameter of the pistons 12 while their internal diameters are greater than the external diameter of the second locator elements 24.
  • the internal and external diameters of the second intermediate element 33 are greater, respectively, than the internal and external diameters of the first intermediate element 32.
  • the two intermediate elements 32 and 33 therefore allow the relative piston 12 to remain resting against the relative second locator surface 24a and their different diameters allow the piston itself to move along a wide travel with respect to the second locator element 24.
  • the head 12a of the pistons 12 is therefore not solid but has a through hole through which the relative locator element 24 is fitted.
  • This shape of the fastening means 21 allows the optimisation of the hydraulic balancing of the pistons 12 and allows them to shift with respect to the inner ring 16 even in the presence of warmer contact areas than others, e.g. due to the reduction in meatus of oil in these areas. In these conditions, in fact, the pistons 12 rotate around the hot areas, which therefore act as a hinge, positioning themselves autonomously in a different area and thus allowing them to cool.
  • the machine 1 comprises, then, at least one connection joint 25, placed between the rotor element 7 and the inner ring 16 and suitable for connecting them in rotation around the respective axes 8 and 17.
  • the joint 25 is therefore suitable for transmitting the rotational motion from the inner ring 16, which, as we have seen, takes the motion from the shift of the pistons 12 along the relative sliding directions 13, to the rotor element 7.
  • one between the inner ring 16 and the joint 25 comprises at least a first seat 26 and the other supports in rotation at least a first revolving element 27 rotating around a relative axis 27 a, where the first revolving element 27 is fitted inside the first seat 26 and is suitable for cooperating with it to transmit a drive torque to the joint 25.
  • one between the joint 25 and the rotor element 7 comprises at least a second seat 28 and the other supports in rotation at least a second revolving element 29 rotating around a relative axis 29a, where the second revolving element 29 is fitted inside the second seat 28 and is suitable for cooperating with it to transmit a drive torque to the rotor element 7.
  • the revolving elements 27 and 29 come into contact with at least a containment wall 26a, 28a which delimits the relative seat 26, 28 and roll along it around their respective axes 27a, 29a during the rotation of the inner ring 16 and the rotor element 7.
  • Each seat 26, 28 also has two containment walls 26a, 28a facing and spaced apart from each other, the revolving elements 27, 29 being positioned between the relative containment walls 26a, 28a.
  • the containment walls 26a, 28a extend substantially parallel to the axes 27a, 29a of the revolving elements 27, 29.
  • the distance between the containment walls 26a, 28a of a relative seat 26, 28 is bigger than the diameter of the revolving element 27, 29 fitted in the seat itself, in such a way that the revolving element itself comes into contact with only one containment wall 26a, 28a and is free to roll along it. This is particularly advantageous as it prevents the relative friction between the revolving element 27, 29 and the relative seat 26 ,28, consequently reducing the loss of energy due to friction.
  • the joint 25 therefore carries out a rotary-translational movement in the chamber defined by the bearing structure 2, 3 and the position of its axis of rotation varies substantially with continuity both with respect to the joint itself and to the axes 8, 17.
  • the revolving elements 27, 29 are therefore integral in rotation to the inner ring/ oint/rotor element which supports them and are released in rotation with respect to them around the relative axes 27a, 29a.
  • the revolving elements 27, 29 have a substantially circular section.
  • the revolving elements 27, 29 have a substantially cylindrical shape and their outer lateral surface comes into contact with the relative containment wall 26a, 28a.
  • the outer lateral surface of the revolving elements 27, 29 defines at least a line of contact on the relative containment wall 26a, 28a.
  • FIG 7 by tracing a plane with a section substantially perpendicular to a containment wall 26a, 28a and passing through the axis of rotation of the relative revolving element 27, 29, we can see how the contact between them defines a continuous segment, identified by letter d in the figure.
  • the thickness of the revolving elements 27, 29, here with the term thickness meaning the dimension along the relative axis 27a, 29a, is greater than the thickness (measured along the same direction) of the corresponding wall 26a, 28a on which they rest, in order to come into contact with such wall 26a, 28a along its whole extension thus ensuring uniform distribution of the load on it.
  • This ratio between the thickness of the revolving elements 27, 29 and that of the walls 26a, 28a allows the joint to support high loads and high rotational speeds.
  • the revolving elements 27, 29 are preferably made up of sliding or roller bearings and the relative containment walls 26a, 28a come into contact with their outer ring.
  • the axis 27a of the first revolving element 27 is substantially parallel to the axes 8, 17 and is offset at least with respect to the second axis 17; similarly, the axis 29a of the second revolving element 29 is substantially parallel to the axes 8, 17 and is offset at least with respect to the first axis 8.
  • the seat 26 and 28 are arranged transversally to each other and, preferably, are arranged at right angles to each other.
  • one between the inner ring 16 and the joint 25 supports in rotation at least two first revolving elements 27 around the relative axes 27a, which are arranged parallel and spaced apart from each other.
  • at least one of the axes 27a, preferably both, is offset at least with respect to the second axis 17.
  • the other between the inner ring 16 and the joint 25 comprises at least two first seats 26, each of which is suitable for housing a relative first revolving element 27. More specifically, the two first seats 26 have an elongated shape and are substantially aligned together along the respective directions of longitudinal extension.
  • one between the rotor element 7 and the joint 25 supports in rotation at least two second revolving elements 29 around the relative axes 29a, which are arranged parallel and spaced apart from each other.
  • at least one of the axes 29a, preferably both, is offset at least with respect to the first axis 8.
  • the other between the rotor element 7 and the joint 25 comprises at least two second seats 28, each of which is suitable for housing a relative second revolving element 29.
  • the two second seats 28 have an elongated shape and are substantially aligned together along the respective directions of longitudinal extension.
  • the machine 1 comprises two second revolving elements 29 which are fitted in the same second seat 28 which is therefore unique.
  • the seats 26 and 28 are defined on the joint 25, while the inner ring 16 and the rotor element 7 support the first and the second revolving elements 27 and 29, respectively.
  • the joint 25 comprises two first seats 26 and two second seats 28, where the first seats 26 are arranged in a substantially aligned way to each other and at right angles to the second seats 28, the latter being substantially aligned together.
  • each seat 26, 28 is defined by a relative through slot and having at least one blind end.
  • the joint 25 therefore has four through slots, each with at least one blind end, where each of the said slots is arranged substantially at right angles to the adjacent slot.
  • Each first seat 26 is therefore angularly followed and preceded by a relative second seat 28, where the first and second seats 26 and 28 are angularly staggered by 90° to each other.
  • the joint 25 has an external profile 25a and a through hole 30 defining an internal profile 2 b.
  • the first and second seats 26 and 28 are arranged on opposite sides with respect to the hole 30.
  • the second seats 28 are defined along the internal profile 25b and have at least an open end corruTiunicating with the hole 30 while the first seats 26 are external to the internal profile 25b, i.e. they do not face on the hole 30.
  • This particular arrangement of the second seats 28 allows to obtain a high compactness of the unit, maintaining the masses at play as close as possible to the axis of rotation of the joint in order to achieve a high number of rpm and at the same time reduce vibration.
  • the first seats 26 are defined along the external profile 25a and have an end which is open towards the outside. Pn the alternative embodiment represented in figure 6, on the other hand, the first seats 26 define a slot having an elongated shape which is closed to both ends. This particular embodiment allows to increase the stiffness of joint 25.
  • the first revolving elements 27 are arranged on diametrically opposite sides of the inner ring 16 and the second revolving elements 29 are arranged on diametrically opposite sides of the rotor element 7.
  • the first revolving elements 27 are therefore integral in rotation to the inner ring 16 around the second axis 17 and are mobile in rotation with respect to it around the relative axis 27a.
  • the second revolving elements 29 are integral in rotation to the rotor element 7 around the first axis of rotation 8 and are mobile in rotation with respect to it around the relative axis 29a.
  • the revolving elements 27 and 29 are of the type of a sliding or roller bearing.
  • the revolving elements 27 and 29 comprise an outer ring suitable for contacting the containment walls 26a, 28a of the relative seat 26, 28 and fit mobile in rotation on a relative inner ring integral to a pin defining the relative axis 27a, 29a of rotation.
  • the second case i.e. in the case of a roller bearing, between the inner ring and the outer ring rollers or balls are placed which are coupled in a rotoidal manner to the rings themselves.
  • the inner rings of the revolving elements 27 and 29 can be fixed integrally to the inner ring 16 or to the rotor element 7 which supports them via screw means or, alternatively, using a Seeger ring.
  • At least one of the revolving elements 27 and 29, preferably each of them, comprises at least one layer of an elastically yielding material (not visible in detail in the figures) which is suitable for dampening any vibrations which can occur during the rotation of the inner ring 16 and of the rotor element 7.
  • the layer of elastically yielding material has a ring shape and is placed between the external surface of the relative revolving element 27, 29 and the relative axis 27a, 29a of rotation. This layer of elastically yielding material is therefore placed between the inner ring and the outer ring of the relative revolving element 27, 29, coaxially to it.
  • the angular position of the distributor 4 is modified in order to anticipate or delay the injection phases into the chambers or the discharge phases with respect to the two dead points of the pistons 12.
  • the phase may need to be corrected, as known to the experts in the field, due to the presence of hazardous spaces, variations in pressure, displacement, speed, etc.
  • by rotating the distributor 4 by 180° the motion of the rotor element 7 is inverted.
  • it may be required to axially move the distributor 4 along the first axis 8.
  • the pistons 12 move radially between an upper dead point and a lower dead point in the relative chambers 11.
  • the pistons themselves move along a direction substantially perpendicular to the sliding direction itself in order to adapt to the geometrical conditions occurring during operation, so as to prevent misalignment with respect to the relative chambers 11.
  • the pistons 12 move along the first locator surface itself in order to position themselves in "colder" areas, i.e. in areas where there is a lubricant film and which ensure a correct hydraulic balancing. More specifically, as stated above, the areas of the first locator surface 22a which may be heated due to the friction with the head 12a of the relative piston 12 and which would not therefore allow the correct relative movement between the parts in contact, as well as a correct balancing of the forces, act as a hinge around which the piston itself moves.
  • the pistons 12 are therefore arranged autonomously in correspondence to the "colder" areas of the first locator surface 22a, thus allowing the "hot” areas to cool down. In this way there is a substantially uniform exploitation of the first locator surface 22a, which ensures a correct hydraulic balancing of the forces acting on the pistons 12 as well as a correct lubrication of the parts in contact and mutually moving.
  • the movement of the pistons 12 with respect to the inner ring 16 along a direction transversal to their sliding direction 13 ensures that the point in which their force is discharged is misaligned with respect to the sliding directions themselves, thus producing a tangential component which brings the inner ring 16 in rotation around the second axis 17.
  • the seats 26 and 28 move with respect to the revolving elements 27 and 29 fitted in them. More specifically, depending on the direction of rotation of the joint 25, the revolving elements 27 and 29 come into contact with their outer surface with one of the containment walls 26a, 28a of the relative seat 26, 28.
  • the relative shift of the seats 26, 28 with respect to the revolving elements 27, 29 causes the rotation of the latter around their respective axes 27a, 29a due to the contact of their containment walls 26a, 28a with the relative outer surfaces.
  • the machine according to the invention is therefore considerable more silent than the machines of known type.
  • the machine greatly facilitates the sizing and production of the connection joint between the inner ring and the rotor element compared to known machines. This is due to the fact that the rotational motion transmission between the inner ring and the distributor element occurs by contact between a cylindrical body and a flat surface and no longer between two flat surfaces. This ensures correct transmission of motion and forces even in the presence of imperfect planarity of the containment walls or lower working tolerances than those needed for the machines used until now.
  • the relative joint can therefore be sized in order to make it considerably lighter than the joints of the known machines, thus also reducing production costs and the weight of the inertial masses at play.
  • the machine according to the invention in use, allows to maintain a correct lubrication of the parts in contact and mutually moving.
  • the fastening means connecting the pistons to the inner ring offer better balancing than known machines of the hydraulic forces acting on the pistons themselves and more uniform wear of the parts in contact.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Reciprocating Pumps (AREA)
  • Hydraulic Motors (AREA)

Abstract

L'invention concerne une machine volumétrique tournante (1) à pistons radiaux, dans laquelle la bague interne (16) ou le joint (25), couplant en rotation la bague interne (16) et l'élément rotor relatif (7), comprend au moins un premier siège (26), et l'autre parmi la bague interne et le joint supporte en rotation au moins un premier élément rotatif (27) autour d'un axe relatif (27a), le premier élément rotatif (27) étant ajusté dans ledit premier siège (26) et coopérant avec lui pour transmettre un couple au joint (25). L'élément rotor (7) et/ou le joint (25) comprennent au moins un second siège (28) et l'autre parmi l'élément rotor et le joint supporte en rotation au moins un second élément rotatif (29) autour d'un axe relatif (29a), le second élément rotatif (29) étant ajusté dans le second siège (28) et coopérant avec lui pour transmettre un couple à l'élément rotor (7). Le premier et le second élément rotatif (27, 29) tournent autour de leur axe respectif (27a, 29a) le long d'au moins une paroi de retenue (26a, 28a) délimitant les sièges respectifs (26, 28) pendant la rotation de la bague interne (16) et de l'élément rotor (7).
PCT/IB2013/053212 2012-04-26 2013-04-23 Machine volumétrique tournante à pistons radiaux WO2013160835A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP13727991.5A EP2859219A1 (fr) 2012-04-26 2013-04-23 Machine volumétrique tournante à pistons radiaux

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
ITMO2012A000112 2012-04-26
IT000112A ITMO20120112A1 (it) 2012-04-26 2012-04-26 Macchina volumetrica rotativa a pistoni radiali

Publications (1)

Publication Number Publication Date
WO2013160835A1 true WO2013160835A1 (fr) 2013-10-31

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Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/IB2013/053212 WO2013160835A1 (fr) 2012-04-26 2013-04-23 Machine volumétrique tournante à pistons radiaux

Country Status (3)

Country Link
EP (1) EP2859219A1 (fr)
IT (1) ITMO20120112A1 (fr)
WO (1) WO2013160835A1 (fr)

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2556717A (en) * 1944-11-14 1951-06-12 Elek K Benedek Pump or motor
US4131056A (en) * 1977-12-15 1978-12-26 Fiat-Allis Construction Machinery, Inc. Pilot controlled variable displacement fluid motor
WO2003060321A1 (fr) 2002-01-16 2003-07-24 Ecotec S.R.L. Machine rotative a pistons radiaux

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2556717A (en) * 1944-11-14 1951-06-12 Elek K Benedek Pump or motor
US4131056A (en) * 1977-12-15 1978-12-26 Fiat-Allis Construction Machinery, Inc. Pilot controlled variable displacement fluid motor
WO2003060321A1 (fr) 2002-01-16 2003-07-24 Ecotec S.R.L. Machine rotative a pistons radiaux

Also Published As

Publication number Publication date
EP2859219A1 (fr) 2015-04-15
ITMO20120112A1 (it) 2013-10-27

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