EP0106808B1 - Machine hydrostatique à pistons radiaux et cylindrée variable - Google Patents

Machine hydrostatique à pistons radiaux et cylindrée variable Download PDF

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Publication number
EP0106808B1
EP0106808B1 EP83830132A EP83830132A EP0106808B1 EP 0106808 B1 EP0106808 B1 EP 0106808B1 EP 83830132 A EP83830132 A EP 83830132A EP 83830132 A EP83830132 A EP 83830132A EP 0106808 B1 EP0106808 B1 EP 0106808B1
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EP
European Patent Office
Prior art keywords
shaft
cam
machine
movable body
machine according
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.)
Expired
Application number
EP83830132A
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German (de)
English (en)
French (fr)
Other versions
EP0106808A2 (fr
EP0106808A3 (en
Inventor
Gualtiero Maurer
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Individual
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Individual
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Publication of EP0106808A3 publication Critical patent/EP0106808A3/fr
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    • 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
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/12—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by varying the length of stroke of the working members
    • F04B49/123—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by varying the length of stroke of the working members by changing the eccentricity of one element relative to another element
    • F04B49/125—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by varying the length of stroke of the working members by changing the eccentricity of one element relative to another element by changing the eccentricity of the actuation means, e.g. cams or cranks, relative to the driving means, e.g. driving shafts
    • F04B49/126—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by varying the length of stroke of the working members by changing the eccentricity of one element relative to another element by changing the eccentricity of the actuation means, e.g. cams or cranks, relative to the driving means, e.g. driving shafts with a double eccenter mechanism
    • 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
    • F04B1/06—Control
    • F04B1/07—Control by varying the relative eccentricity between two members, e.g. a cam and a drive shaft

Definitions

  • This invention relates to a hydrostatic machine with radial pistons.
  • hydraulic machine is used to design a machine which can be a motor or an operator, for example a motor or a pump in which a hydraulic fluid, generally oil, exchanges pressure energy with an element. mechanical.
  • hydraulic machine In the word "hydrostatic machine” one must also design the hydraulic transmissions which include a motor and a pump.
  • variable displacement machine solved in particular many problems of oleostatic transmission, in particular is widely used today the combination of a variable displacement pump and a fixed displacement motor, since it results easier to intervene on the variability of the pump to obtain in the motor, with fixed displacement, a continuous variation of the number of revolutions and consequently the inverse continuous variation of the driving torque.
  • variable displacement motor By having a variable displacement motor, obvious constructive advantages are obtained when it is supplied with a fixed mounted pump, for example a simple gear pump, coupled to a heat or electric motor. .
  • variable displacement pump If, in addition, a variable displacement pump is also available, the functional characteristics of the hydraulic transmission greatly increase.
  • the displacement In machines with axial pistons the displacement varies by continuously varying the inclination of the axis of the cylinder-holder body relative to the engine axis, or by varying a control plate for the axial pistons, while in the radial piston machines the displacement is obtained by varying the eccentricity of the eccentric which determines the stroke of the radial pistons.
  • a known embodiment provides a movable eccentric back and forth, controlled by small hydraulic pistons inserted in the body of the shaft on which this eccentric is mounted.
  • the object of this invention is a hydrostatic machine with radial pistons having a shaft joined to an eccentric cam, with variable eccentricity, in the manner of obtaining a hydraulic machine with variable displacement which, among other things, can be automatically self-adjusted to adapt to varying load conditions.
  • This hydrostatic machine is configured in its general layout as a radial piston machine of the type generally used as a hydraulic motor with several radial pistons with shaft provided with eccentric cam and which comprises a carcass in which the cavities of the cylinders are drilled and a cam eccentric circular, the axis of symmetry which is parallel to the axis of rotation of the machine, linked to the shaft in the axial direction and which has an eccentricity with respect to the axis of the shaft and therefore of the machine.
  • the eccentric cam is pivotally movable about the axis of a movable body interposed between the shaft and the eccentric cam, which is in turn pivoted around the same axis, which is parallel to the axis of the shaft and to the axis of symmetry of the cam, so that in a rotation of the eccentric cam around the axis of the body mo bile, the center of the cam passes from a position where it is located at a distance from the shaft in which the resulting eccentricity is the difference of the two eccentric distances, to another diametrically opposite position where the two eccentricities lie between them.
  • the distance from the center of the cam to the shaft axis measures the effective eccentricity that this cam has in relation to the shaft.
  • eccentricity Since in the machine of this invention this eccentricity does not have a fixed value, but variable, according to the loading conditions of the machine, as will be better explained, following the description and the claims, the word “eccentricity” will be used to indicate the instantaneous and variable distance between the axis of symmetry of the eccentric circular cam (this means the axis which passes through its center) and the axis of the shaft.
  • the word "disaxation" and its derivatives will be used to indicate the distance between the axis of the movable body (which is also the axis of rotation of the eccentric cam) and the axis of the shaft, and this distance is a characteristic which has a fixed value, this means that it is a constructive characteristic of the machine.
  • This movable body is also engaged with the shaft and the eccentric cam respectively with screw couplings, at least one of which is with reversible screws, these screws having cylindrical helix threads with different geometric characteristics (one of these screws can be simply axial grooves); as well as a relative rotation between the shaft and the eccentric cam corresponds to a displacement of the movable body along its axis.
  • the movement of the movable body to cause the variation in the displacement of the machine can happen through actuation from the outside, for example, through an oleodynamic control.
  • the machine of the invention has an offset between the axis of the shaft and the axis of the movable body.
  • this last distance and this offset may be different from each other, and this is part of the scope of this invention, to facilitate description and as a preferred embodiment it is then assumed that this distance and this offset are of the same length.
  • the machine of the invention generally comprises: a shaft 1 with axis A, an eccentric disc 2 or cam with axis of symmetry B and a movable body 3 with axis of rotation C.
  • the movable body 3 is coupled to the shaft 1 and the cam 2 with screw coupling 4 and 5 respectively.
  • the screws 4 and 5, according to the invention, must be of different threads and at least one must be reversible.
  • the thread 4 is represented as a coupling with axial slots, as well as the shaft 1 and the movable body 3 are coupled with axial sliding, without reciprocal rotation.
  • the shaft 1 and the cam 2 are coupled so as not to move axially with respect to each other, by mechanical construction, but they can roll one compared to each other.
  • At least one elastic element pushes the mobile body 3 towards an axial direction.
  • the axis C of the movable body 3 is offset from the axis A of the shaft by a distance d.
  • the axis B of the cam 2 is disposed at the same distance d from the axis C of the movable body 3.
  • cam 2 is coupled on its periphery with radial pistons (not shown) which are arranged in a conventional manner in a cylinder block (not shown).
  • the fixed element of the machine can be the carcass, in this case the shaft-cam assembly rotates around the axis of the shaft, or else the carcass is the rotating element and the assembly camshaft is fixed.
  • the shaft-cam assembly is not rigid, but the cam 2 can take different positions by varying its eccentricity while the shaft 1 can be actually fixed.
  • the axis of symmetry B of the cam 2 can move along the circle F, having as its center the axis C of the moving body 3.
  • the value of the torsional moment also has a sinusoidal shape, and consequently the axial thrust of the mobile body 3 will also have a sinusoidal shape due to the torsional moment.
  • this torsional moment is none other than the motor moment which manifests itself in the machine as a consequence of the value of the pressure in the cylinders, the motor moment it takes to overcome the resistant moment.
  • the curves p ,, P2 ; ... p n illustrated in the 4 th image (fig. 4), show on the ordinate the sinusoidal shape of the axial thrust values H, caused by a torsional moment produced by the action of various pressures in the cylinders.
  • Each curve represents a constant pressure at the variation of the angle 0 (on the abscissa) and therefore of the eccentricity.
  • a variation of the pressure will thus obtain a family of curves each of which is at constant pressure and these curves are arranged with increasing pressure upwards.
  • the line m shown in the 4 th picture (Fig. 4) which starts from the origin, represents the characteristic, for example linear, elastic imployé means that provides a Z reaction (ordinate).
  • This line has an inclination which depends on the rigidity of the elastic means adopted.
  • the points Q of intersection between this line and the curves of the axial thrust H due to the moment of torsion are thus shown.
  • intersection points Q represent the point of equilibrium between the pressure on the cam 2 (torsional moment) and the reaction of the elastic means depending on the rotation 0 of the cam 2.
  • the machine which adjusts itself according to this invention has subsequent notable advantages which derive from its intrinsic properties.
  • the movable body 3 as already said, is characterized in that it has two screw threads with different geometric characteristics on two different parts of its surface.
  • It may consist of a cylindrical element which has two cylindrical ends on the surface of which these threads are executed with screws engaging with the shaft and with the cam, as shown in the first image. (Fig. 1).
  • Another embodiment consists in making the movable body in the form of a sleeve with a thread on the outside and the other inside the hole of the sleeve as illustrated with 8 in the 5th image (fig. 5).
  • Another embodiment provides a body generically in the form of a cylindrical mushroom in which an external thread is executed on the external surface of the cylinder which constitutes the cap of the mushroom and another thread on the cylindrical tail of this mushroom.
  • This embodiment is illustrated with the 9 in the 5th image and with 10 in the 7 "" "'image.
  • each of these embodiments corresponds to the conjugate form of the couplings in the shaft or in the eccentric cam to guarantee the correct functioning of the screw coupling.
  • the embodiment of the elastic means is as wide as possible, since it is requested that these elastic means oppose the movement of this movable body being engaged between the latter and the shaft or the cam.
  • These elastic means can be cylindrical springs, springs with valuts, springs with cut or undercut, which are expediently requested from suitable appendages applied to the movable body and the same springs can be housed inside or inside. outside of the shaft or cam.
  • a particularly interesting embodiment plans to replace the springs, which are too heavy and bulky, with a servo-amplifier amplifier of the characteristic of a small calibrated spring, leads to control, depending on the deformation of the spring, the value of the pressure oil which acts on a piston which contrasts the axial movement of the moving body and therefore the rotation of the eccentric cam.
  • a further embodiment provides for the use of the elastic qualities of a compressed gas, for example by placing in fluid communication a hydraulic accumulator with a variable volume cavity defined by a piston which moves in a cylinder, the piston and the cylinder being respectively joined to the movable body and to the shaft or to the movable body and to the cam.
  • the hydraulic accumulator which has very contained dimensions, can be installed outside the machine and can find a favorable position very close to it.
  • the eccentric cam is pivotally movable relative to the shaft to which it is coupled with its own means which allow it to rotate but prevent it from axial movements.
  • connection provides for a cylindrical sliding accomplishment with clean lateral shoulders to prevent axial displacements.
  • This cylindrical seat is executed on the, or in the head of the shaft and has an axis which coincides with the axis of the movable body and a corresponding housing in the cam to the axis which coincides with the axis of eccentricity of drug.
  • the large load on the eccentric cam and the slowness of the rotation can be such as to drive out all the oil from the two surfaces until contact thus obstructing the regular functioning of the device.
  • radial piston machines in addition to automatic non-return valves, three types of distributor for the actuating fluid of the cylinders are used, in particular the axial type distributor with cylindrical rotation, the plain rolling axial type distributor, and the pentagonal distributor mounted on the peripheral surface of the eccentric cam.
  • the distributor rotates in axis with the drive shaft, while the cam rotates in axis with the movable body
  • the value of the angle of equilibrium is no longer determined by a well-determined pressure but depends significantly on the constructive and functional parameters of the machine such as friction, variations in oil viscosity and ecc work tolerances.
  • One possible means for modifying the elastic characteristic of the elastic means is to use a pressure control fluid to increase or decrease the force, for example using a piston employed by these elastic means and which moves in a cylinder.
  • This control fluid can come from an own hydraulic power plant, or can be taken from the supply line and therefore have the same variable supply pressure depending on the operating conditions.
  • a particularly effective solution is to control the pressure of this control fluid through a throttle subject to the axial movement of the movable body, thus obtaining an exact correspondence between the position of the movable body which is a function of the supply pressure and the value of the pressure of the control fluid leaving the choke.
  • the elastic means are dimensioned in such a way as to have a reduced residual response by an assigned quantity, as well as these elastic means have the function of reducing, to the desired extent, the positioning force necessary for move the moving body on command, regardless of the load conditions.
  • This eccentric cam 15 is movably coupled to the shaft 12 being rotatably supported for example through rolling bearings 16 by a cylindrical head 17, preferably conical, projecting from the shaft 12, with axis C eccentric relative to axis A of tree 12.
  • the eccentric cam 15 has a cylindrical recess 18, preferably conical, complementary to the head 17 of the shaft 12, with its axis coinciding with the axis C of offset.
  • cam 15 is secured, through bolts 19, an enlarged head 20 of a reversible screw 21 having its axis coincide with the axis C of offset of the recess 18 and therefore of the cam 15, which screw is disposed at the inside this recess 18, the other end 23 of this screw 21 being rotatably supported in a seat 22 executed in the shaft 12.
  • the reversible screw 21 is engaged in the hole 24 of a cylindrical sleeve 8 which constitutes the body mobile, this sleeve 8 having on its outer surface rectilinear slots 25 or helix with very long pitch.
  • the slots 25 of the sleeve 8 are engaged in the corresponding slots 26 of an axial hole in the shaft 12, the axis of this hole being coincident with the axis C of the screw and therefore eccentric with respect to the axis A of the shaft 12, so that this hole results in an axis with the eccentric head 17 of the shaft 12.
  • the hole in the shaft 12 opens at the other end into a recess 27 with an enlarged diameter in which slides, with fluid holding, a piston disc 28 which is secured, through an appendage 29, to the sleeve 8.
  • This piston disc 29 is also crossed in the center, from the other end 23 of the screw 25 which in this case is executed with a smooth tail.
  • this recess 27 with an enlarged diameter is another housed a compression spring 30 which acts between this piston disc 28 and the shaft 12.
  • the eccentric cam 15 rotates by a certain angle and the sleeve 8 is returned by the screw 21 secured to the eccentric 15, so as to be guided to slide in the annular gap between the screw 21 and the head 17 of the shaft, driving the disc of the piston 28 which, in addition to pressing the spring 30, also reduces the volume of the widened recess 27.
  • This enlarged recess 27 is placed in fluid communication, preferably with a hydraulic accumulator (not shown) from which the elastic compression of the gas it contains is used.
  • the cylinder chamber located on the other side of the piston disc 28, when it moves in the enlarged recess 27, can be used to modify the characteristic of the spring by sending oil into this chamber at controlled pressure.
  • An annular distributor 31 is arranged around the shaft 12. Since the disc 15 moves angularly relative to the shaft 12, the distributor also must perform the same angular rotation around the shaft 12.
  • the eccentric cam 15 has a button 32 tilting laterally, which engages in a radial slot 33 executed in the distributor 31, as it carries it in rotation despite the eccentricity between the eccentric cam 15 and the axis A of the tree 12.
  • the pistons 37 receive the thrust in the cylinders of a hydraulic fluid under pressure and transmit it through suitable hydrostatic pads to the eccentric cam 38 by rotating it.
  • the eccentric cam 38 is pivotally engaged on the shaft 35, being rotatably supported for example through a mechanical sliding coupling, on a cylindrical or slightly conical head 39, projecting from the shaft 35 and with axis C eccentric relative to axis A of the shaft 35.
  • the disc 38 has a complementary recess 40, cylindrical or slightly conical, with an axis coinciding with the axis of misalignment and a central protuberance 41 inside this recess 40 in which a threaded hole 42 with reversible screw is made having the same axis C of offset.
  • this screw 43 which constitutes the movable body 9
  • this screw 43 has, integral with itself at the other end, an appendage 44 with disc or mushroom shape which has on its peripheral edge straight threads 45 or with long pitch propeller.
  • the shaft 35 inside has an axial cylindrical recess 46, the axis of this recess being coincident with the axis C of the screw 43, and therefore off-center with respect to the axis A of the shaft 35.
  • the inner surface of the recess 46 has slots 47 in which the slots 45 of this appendage 44 in the form of a mushroom are engaged.
  • This recess 46 opens into the cylindrical projecting head 39.
  • the mushroom disc 44 in turn is integral with a peripheral mantle 48 thus defining a recess 51 of the cylinder in which a counter-cylinder 49 is engaged slidingly and with fluid resistance 49 housed in the recess 40 of the eccentric cam 38.
  • the eccentric cam 38 rotates by a certain angle, while the shaft 35 is retained by the load applied and the screw 43 is returned to the hole 40 of the eccentric 38, driving the mushroom disc 44 and reducing the volume of the cylinder recess 51 and compressing a spring 50 disposed inside this recess 51.
  • This cylinder recess 51 is arranged in fluid communication with a hydraulic accumulator (not shown) from which the elastic properties of the gas are used and which, however, operates in parallel with the spring.
  • the embodiment presented provides for a rotating planar distributor 52 and yet the planar distributor 52 must be rotated in synchro- nie with the eccentric cam 38, while this cam 38 rotates with the shaft 35. But during the rotation of the shaft, this cam performs small angular displacements relative to the shaft.
  • the eccentric cam 38 has a cylindrical projection 53 in axis with the screw 43, this projection 53 being housed in a cylindrical sleeve 54 suitably supported in the carcass 34 and in axis with the axis A of the shaft 35.
  • the housing hole of the projection of the sleeve 54 has, on the contrary, its axis displaced by the same offset as the axis C of the screw 43, as are the angular displacements of the eccentric cam 38 during rotation.
  • a radial slot 55 In the end part of the cylindrical projection 53 is executed a radial slot 55 in which a sliding prismatic shoe 53 is engaged, executed in the end part of a small shaft 57.
  • This small shaft in turn drives the disc to distribute the rotating plane 52.
  • FIG. 7 discloses an embodiment of the machine according to this invention, as Working motor fixed shaft and rotating casing mounted within a wheel of a vehicle.
  • a rotating carcass 58 coaxial with the axis A of the shaft 59, and therefore of the machine, are defined recesses 60 of cylinders in which the pistons 61 radially movable slide back and forth.
  • This eccentric cam 62 is pivotally engaged with the shaft 59, being rotatably supported, for example with a mechanical sliding coupling by means of a counter-shaft 65 integral with the disc and which rotates a hole 66 executed in the shaft 59 having the axis C eccentric with respect to the axis A of the shaft.
  • This countershaft 65 is integral with a part of the disc 62 and on the other hand with a reversible screw 67, the axis C of the screw coincides with the axis of the countershaft, being offset from the axis of symmetry of the eccentric disc.
  • the reversible screw 67 is engaged in a threaded hole 68 executed in the central tail 69 of a cap 70 in the form of a mushroom which constitutes the movable body 10.
  • This cap 70 has on the peripheral edge threads 71 straight or with long pitch propeller, which engage in axial sliding in a cylindrical recess 72 executed in an enlarged part 73 of the shaft, the axis of this recess 72 being coincide with the axis C of the screw, therefore off-axis with respect to the axis A of the shaft.
  • the front surface of this recess of the shaft has threads 74 in which the threads 71 of the cap 70 in the form of a mushroom are engaged.
  • the peripheral mantle 74 of the cap delimits a recess 76 of the cylinder in which a counter-cylinder 77 is engaged in sliding and fluid-holding 77 and in turn mounted on a seat 78 executed on the counter-shaft 65 in axis with the screw 67 .
  • the eccentric cam 62 rotates by a certain angle while the shaft 59 is fixed, and the screw, bending into the hole in the tail, recalls the cap in the form of fungus by reducing the volume of the cylinder recess.
  • This cylinder recess is full of oil which in this way is pressurized and slows down the rotation of the screw.
  • the increase in oil pressure is transmitted through a hole 79 made in the tail, also in the recess of the hole 68 screw threaded and therefore acts on a small piston 80 which slides with fluid holding in a hole axial 81 executed centrally with the screw 67 and which passes inside the counter-shaft 65 and the eccentric cam 62.
  • the small piston 80 is contrasted by a calibrated and calibrated spring 82 housed inside the axial hole 81. Under the action of the oil pressure, the small piston 80 compresses the spring 28 so that the pressure which prevails in the cylinder recess is essentially a linear function of the deformation of the spring.
  • the small piston 80 has inside a recess at the bottom of which is provided a discharge hole 83 which has a conical seat.
  • This conical seat by effect of the reaction of the calibrated spring on the small piston, is held normally closed by a small cone head 84, supported at one end of a bar 85, the other end of which controls a valve of high pressure 86 normally closed, outside placed in communication with a source of oil under pressure.
  • the recall of the screw corresponds to an increase in the pressure in the cylinder recess and therefore a displacement of the small piston in the direction of compressing the calibrated spring 82.
  • the cap 70 can thus be attracted by the screw until when the pressure inside the cylindrical recess balances the action of the spring on the small piston, followed by closing of the conical seat.
  • a reduction in the action of the screw on the cap corresponds to an instantaneous drop in pressure in the cylinder recess and the spring acting against the small piston, by means of the bar, opens the valve 86 of high pressure, allowing the oil to enter the cylinder recess, until the spring action is rebalanced.
  • the device constituted by the small piston, by the bar and by the high pressure valve functions in the manner of a servomechanism amplifying the elastic characteristic of the calibrated spring.
  • the axial hole 81 also serves as a discharge channel of the oil supplied to the cylinders and a small hole 88 made at the bottom of the axial hole makes it possible to drain the oil drawing which fills the carcass during operation.
  • the carcass has at its periphery a circular flange 89 provided with holes 90 to allow mounting to the tire of a vehicle wheel.
  • the shaft has at its exterior a thread 91 so that it can be supported in a keeper 92 for mounting to the suspensions of a vehicle, by means of bolts which pass through the holes 93.
  • Flexible conduits, joined to the mouths 94 allow to supply and discharge the oil.
  • the machine according to this invention finds its use in all fields in which pumps or hydraulic motors are used which can operate either as a pump or as a motor.
  • an advantageous embodiment provides a machine with the fixed shaft and rotating carcass, and by equipping this cylinder block with a strip or a tire, a compact driving wheel is obtained which self-adjusts for a vehicle. In a vehicle, the four wheels can thus be easily driven.
  • the hydraulic braking of the vehicle can also be obtained, since these machines behave like pumps whenever the external moment exceeds the moment of the machine, in the case where the energy of the pumped fluid can be immagined in an accumulator hydraulic with gas or dissipated through a properly cooled dissipative valve.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Transmission Devices (AREA)
  • Reciprocating Pumps (AREA)
EP83830132A 1982-06-30 1983-06-28 Machine hydrostatique à pistons radiaux et cylindrée variable Expired EP0106808B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
IT48727/82A IT1189306B (it) 1982-06-30 1982-06-30 Macchina idrostatica a pistoni radiali e cilindrata variabile
IT4872782 1982-06-30

Publications (3)

Publication Number Publication Date
EP0106808A2 EP0106808A2 (fr) 1984-04-25
EP0106808A3 EP0106808A3 (en) 1985-01-09
EP0106808B1 true EP0106808B1 (fr) 1989-11-08

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ID=11268278

Family Applications (1)

Application Number Title Priority Date Filing Date
EP83830132A Expired EP0106808B1 (fr) 1982-06-30 1983-06-28 Machine hydrostatique à pistons radiaux et cylindrée variable

Country Status (3)

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EP (1) EP0106808B1 (it)
DE (1) DE3380826D1 (it)
IT (1) IT1189306B (it)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
NL8500402A (nl) * 1985-02-13 1986-09-01 Schelde Nl Aandrijving van verbruikers aan boord van een schip.
IT1295283B1 (it) * 1997-10-06 1999-05-04 Sabi Pompe E Impianti S R L Regolatore di portata applicabile a pompe dosatrici

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB538230A (en) * 1940-02-02 1941-07-25 Charles Hyland Improvements in or relating to eccentrics
GB577287A (en) * 1943-06-04 1946-05-13 George Walstan Drury Improvements in reciprocating pumps
FR1120102A (fr) * 1955-01-14 1956-07-02 Dispositif de commande d'excentricité

Also Published As

Publication number Publication date
EP0106808A2 (fr) 1984-04-25
IT8248727A0 (it) 1982-06-30
DE3380826D1 (en) 1989-12-14
EP0106808A3 (en) 1985-01-09
IT1189306B (it) 1988-02-04

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