EP3499033A1 - Hydraulische pumpe mit gefassten federkugeln - Google Patents

Hydraulische pumpe mit gefassten federkugeln Download PDF

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Publication number
EP3499033A1
EP3499033A1 EP18212153.3A EP18212153A EP3499033A1 EP 3499033 A1 EP3499033 A1 EP 3499033A1 EP 18212153 A EP18212153 A EP 18212153A EP 3499033 A1 EP3499033 A1 EP 3499033A1
Authority
EP
European Patent Office
Prior art keywords
plate
barrel
drive shaft
pistons
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.)
Withdrawn
Application number
EP18212153.3A
Other languages
English (en)
French (fr)
Inventor
Louis-Claude Porel
François POREL
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.)
Hydro Leduc SAS
Original Assignee
Hydro Leduc SAS
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 Hydro Leduc SAS filed Critical Hydro Leduc SAS
Publication of EP3499033A1 publication Critical patent/EP3499033A1/de
Withdrawn legal-status Critical Current

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Classifications

    • 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
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/20—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
    • F04B1/22—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block having two or more sets of cylinders or pistons
    • F04B1/24—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block having two or more sets of cylinders or pistons inclined to the main shaft axis
    • 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
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/122—Details or component parts, e.g. valves, sealings or lubrication means
    • F04B1/124—Pistons
    • F04B1/126—Piston shoe retaining means
    • 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
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/20—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
    • F04B1/2014—Details or component parts
    • F04B1/2064—Housings
    • 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
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/20—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
    • F04B1/2014—Details or component parts
    • F04B1/2064—Housings
    • F04B1/2071—Bearings for cylinder barrels

Definitions

  • the present invention relates to a hydraulic piston pump.
  • piston pumps adjustable in the direction of rotation, which can rotate either in right rotation or left rotation depending on the PTO to which the pump is confronted.
  • the dispensing ice is symmetrical so that the discharge zone of the pump can become an intake zone and vice versa.
  • the orifices of the distribution yoke are symmetrical in order to be able to receive either an inlet connection or a discharge connection.
  • Such pumps are illustrated for example in FR3012181 .
  • the performance of the pump is sacrificed to allow the choice of the direction of rotation.
  • the suction port being of the same size as the discharge port, because of the symmetry, the suction port then creates a pressure drop at the suction of the pump. This loss of load is detrimental to the performance of the pump. In particular, it reduces the possibility of using the pump at a high rotational speed.
  • Piston pumps are also known in which the pistons have spherical piston heads and the plate has machined housings.
  • the machined housings have a truncated spherical shape.
  • the spherical head has a circular flattened at a large circle perpendicular to the axis of the piston, so that it is possible to penetrate the spherical head in its machined housing when the axes of the head and the housing coincide and that it is no longer possible to bring it out when these axes no longer coincide.
  • the piston head is integral in traction of the machined housing.
  • Such pumps are illustrated for example in FR2692008 .
  • Such pumps are preferably fixed displacement pumps.
  • An object of the present invention is to provide a piston pump rotatable in either right or left rotation without at least some of the disadvantages of the prior art.
  • An object of the present invention is to provide a piston pump with fixed or variable displacement.
  • the hydraulic pump is adaptable to the direction of rotation of the power take-off without loss of efficiency, for example by a 180 ° rotation of the distribution yoke around the axis of the barrel.
  • the breech head can have a wide variety of shapes.
  • the distribution yoke has a substantially cylindrical shape.
  • Both lines can have a wide variety of shapes.
  • both lines can be bent.
  • the inner surface and the outer surface of the distribution yoke, that the two lines connect to one another, may be in planes substantially perpendicular to each other.
  • the two pipes are straight.
  • the inner surface and the outer surface of the distribution yoke, which the two lines connect to each other, can be mutually opposed in a thickness dimension of the distribution yoke.
  • the inner surface and the outer surface of the distribution yoke are substantially parallel to each other.
  • the inner surface is flat and is treated to reduce the coefficient of friction, for example it comprises a bronze coating.
  • the intake and discharge pipes each have a circular arc-shaped section, the two arc-shaped sections being concentric and each extending over a distinct portion of a circle.
  • such a pump further comprises a plurality of spheres fixed on the plate, the pistons each having a rod capable of sliding in the bore and further comprising a head crimping one of said spheres.
  • This form of coupling can be used in pumps of different types: for example in a fixed displacement pump, a variable displacement pump, a reversible cylinder head pump or not.
  • bores are formed on the plate, the pump further comprising lugs fixed to said spheres, the lugs cooperating with the bores formed on the plate.
  • the stem of each piston has a channel extending longitudinally in the rod so as to hydraulically connect the bore and the piston head, in order to lubricate the piston head to facilitate the rotation of the coupling. pistons to the plateau.
  • the lugs are welded to said spheres, such an assembly can be obtained for example by a friction method.
  • the pump further comprises two annular seals mounted on the drive shaft, the pump further comprising a hydraulic leak sensor disposed between the first seal and the second seal so as to emit a signal in response the detection of fluid leakage between the two seals.
  • the signal is a light signal or an electrical signal. Thanks to these characteristics, the first seal isolating the hydraulic chamber of the oil from the vehicle power take-off and the second insulating seal the drive shaft of the hydraulic fluid of the hydraulic chamber, the sensor makes it possible to immediately identify any leakage of engine oil or hydraulic fluid to prevent hydraulic fluid leaking into the engine of the vehicle to avoid flooding the engine of the vehicle or seizing the pump in the absence of hydraulic fluid.
  • the coupling of the pistons to the plate is a spring-type restoring force and / or a pivoting crimping of the pistons on the plate.
  • the relative inclination between an axis perpendicular to the plate and the axis of the barrel is variable.
  • a hydraulic pump is also called variable displacement pump.
  • the inclination of the plate and / or the barrel is adjustable via cylinders.
  • the axis of the drive shaft is not parallel to the axis of the barrel. This is called a broken axle pump.
  • the variable displacement pump is also broken axis, preferably, it is the inclination of the cylinder which is adjustable relative to the axis perpendicular to the plate.
  • the plate and the drive shaft are integral in rotation. According to one embodiment, the plate and the drive shaft are formed in one piece.
  • the drive shaft is orthogonal to the plate, and wherein the barrel is tilting to a position in which it is parallel to the axis of the drive shaft.
  • the hydraulic pump Figures 1 to 6 has several specificities, including a reversible distribution yoke and a special connection between the pistons and the plate.
  • the figure 1 represents the hydraulic piston pump comprising a drive shaft 1 provided with a plate 2.
  • the plate 2 is formed in a plane perpendicular to the axis of the drive shaft 1.
  • the hydraulic pump further comprises a casing 6 of axis inclined with respect to the axis of the drive shaft 1.
  • the housing 6 has a first portion and a second portion.
  • the first portion of the housing 6 has a substantially cylindrical shape about a first axis and comprises the drive shaft 1 whose axis is parallel to this first axis.
  • the first part of the housing 6 is equipped with bearings 20 allowing rotation of the drive shaft 1.
  • the second portion of the housing 6 has a substantially cylindrical shape around a second axis and comprises a distribution yoke 9 whose axis is parallel to this second axis.
  • the first axis and the second axis form a non-zero angle.
  • the distribution yoke 9 is fixed to the casing 6 as will be described later with reference to the Figures 3 and 4 .
  • the hydraulic pump further comprises a barrel 5 adapted to rotate in the casing 6 around the second axis of the casing 6.
  • Cylindrical bores 4 are formed in the barrel 5.
  • the bores 4 are formed parallel to the axis of the barrel 5.
  • the hydraulic pump also comprises a plurality of pistons 3.
  • the pistons 3 are able to slide in the bores 4 formed in a rotating barrel 5 housed in the casing 6.
  • the cylinder 5 bears against the cylinder head 9. Thus, the cylinder 5 is rotated relative to the cylinder head 9.
  • the distribution yoke 9 comprises a guide 16 in the form of a cylindrical hollow formed around the axis of the distribution yoke 9.
  • a compression spring 15 is mounted on a guide pin 14, the spring 15 bearing against the bottom of the distribution yoke 9 and the guide pin 14 bearing against a bore formed in the plate 2, so that the spring 15 maintains the cylinder 5 in abutment against the cylinder head 9.
  • the distribution yoke 9 has a substantially cylindrical shape between two surfaces. One of the two surfaces is a connecting surface 17. The other is a bearing surface 12. The rear face of the cylinder 5 bears on the bearing surface 12 of the distribution yoke 9.
  • the distribution yoke 9 has a friction function on the bearing surface 12.
  • the bearing surface 12 is treated by a bronze melting process so that its coefficient of friction is low.
  • a first duct is an intake duct 8 and a second duct is a discharge duct 13. These two ducts are shown with reference to figures 2 and 6 .
  • the figure 2 is a sectional view according to DD of the figure 1
  • the figure 6 is a sectional view according to EE of the figure 1 .
  • the intake duct 8 connects the connection surface 17 of the distribution yoke 9 at a first end configured to receive an inlet duct A.
  • the first end has a substantially circular cylindrical shape.
  • the intake duct 8 connects the bearing surface 12 of the distribution yoke 9 at a second end which has a cylindrical shape whose base is of substantially circular circumferential arc shape, less than half a turn, at close to the bearing surface 12.
  • the intake duct 8 flares circumferentially.
  • the discharge duct 13 connects the connecting surface 17 of the distribution yoke 9 at a first end configured to receive a discharge pipe B.
  • the first end has a substantially circular cylindrical shape.
  • the discharge duct 13 connects the bearing surface 12 of the distribution yoke 9 at a second end which has a cylindrical shape whose base has a shape of a substantially circumferential arc of less than half a turn, close to of the bearing surface 12.
  • the discharge conduit 13 flares circumferentially.
  • the pressure on the intake duct 8 is generally that of the atmospheric pressure. In order to facilitate the suction of the pump, it is important to minimize the pressure losses on the intake duct 8.
  • the intake duct 8 is therefore dimensioned to create little resistance to the admission of the fluid hydraulic. Also, the intake duct 8 has a section greater than that of the discharge duct 13. This asymmetrical dimensioning therefore reduces the loss of loads compared to a symmetrical dimensioning.
  • the intake duct 8 has a larger section than that of the discharge duct 13 in order to limit the pressure drops.
  • Each bore 4 is provided at its base with a pipe 7.
  • the pipe 7 of each bore 4 of the barrel 5 passes alternately during each rotation turn on the intake duct 8 during the intake phase. then on the discharge pipe 13 during the discharge phase.
  • Each piston 3 has a cubic capacity, the total displacement will be a function of the number of pistons 3 and the relative inclination of the plate 2 relative to the axis of the pistons 3.
  • hydraulic pump can be optionally and reversibly configured as a right or left rotating hydraulic pump.
  • the hydraulic pump may be intended to be mounted on a vehicle power take-off, for example truck.
  • the output of the PTO turn right or left: it is therefore advantageous to offer users the hydraulic pump that can turn in one direction or the other so that they have only one only model in store.
  • the distribution yoke 9 has, as previously described, two ducts 8 and 13 asymmetrical.
  • the cylinder head 9 is adapted to be fixed on the casing 6 in two different ways, as desired:
  • the distribution yoke 9 can be fixed on the housing 6 so that the intake duct 8 is located on the right, and the discharge duct 13 is located on the left from the connection surface 17 of the cylinder head 9, on the section EE.
  • Such an arrangement corresponds to a right rotation, also called a clockwise rotation, and is represented for example on the figures 3 and 5 .
  • the distribution yoke 9 can also be fixed on the casing 6 so that the intake duct 8 is located on the left, and the discharge duct 13 is located on the right from the connection surface 17 of the cylinder head 9 on the EE section.
  • Such an arrangement corresponds to a left rotation, also called counterclockwise rotation, and is represented for example on figures 4 and 6 .
  • the distribution yoke 9 is designed to be fixed between two angular positions offset by 180 ° from each other relative to the casing 6, the two angular positions respectively corresponding to the two possible directions of rotation of the shaft. training 1.
  • the figure 3 illustrates the position of the intake pipe A, when the drive shaft 1 is in right rotation
  • the figure 4 illustrates the position of this intake pipe A when the drive shaft rotates in left rotation.
  • a discharge pipe B is connected to the discharge pipe 13 of the distribution cylinder head 9.
  • the positioning means of the distribution yoke 9 between the position of the figure 3 and that of the figure 4 can be, for example, an indexing screw 44 which can be mounted in one or the other of two orifices 45 and 46 provided in the distribution yoke 9 of the pump, in the direction of rotation of the pump.
  • the screw 44 is shown mounted in the orifice 45.
  • the pump rotates clockwise. In order for the pump to turn counterclockwise, it is necessary to remove the screw 44, to turn the distribution cylinder 9 bearing the inlet and discharge lines B by 180 °, and to fix the screw 44 in the orifice 46.
  • the distribution head 9 180 ° without removing it from the housing 6.
  • the screw 44 may also serve as a key so that, depending on the mounting position of the screw 44, the operator can visually determine what is the direction of rotation of the pump. For this, a visual marker 99 indicating the clockwise direction, or SH, is etched on the cylinder head next to the orifice 45 and a mark 98 indicating the reverse clockwise or SIH is etched on the cylinder head next to the orifice 46.
  • connection also called the coupling
  • the plate 2 has two cylindrical depressions 21.
  • the cylindrical recesses 21 are of axis parallel to that of the axis of the drive shaft 1.
  • the drive shaft 1 and the plate 2 are formed of a single taking.
  • Each piston 3 has an attachment stud 33.
  • the fixing stud 33 is formed of elements of different functions each referenced by a different reference numeral, although these different elements are formed in one piece in the example of the figure 1 .
  • the fixing stud 33 comprises a sphere 32.
  • the sphere 32 is in connection with the plate 2.
  • Each piston 3 comprises a rod 31 whose end 35 forms a crimping.
  • each piston 3 is mounted crimping the sphere 32 of the fixing stud 33.
  • the end 35 thus irreversibly encloses the sphere 32.
  • the rod 31 is able to slide in a bore 4 while the end 35 forming the crimping remains, in operation, external to the bore 4.
  • connection between the spheres 32 and the plate 2 is performed as described below.
  • the sphere 32 is mounted on a cylindrical pin 34.
  • the cylindrical pin 34 has a straight cylindrical shape whose diameter is slightly smaller than that of the cylindrical hollow 21.
  • the sphere 32 is mounted on one of the planes of the cylindrical pin 34.
  • the cylindrical pin 34 and the sphere 32 may be made in one piece or are fixed together by welding, for example friction welding.
  • each fastening stud 33 is introduced into one of the two cylindrical depressions 21 of the plate 2.
  • the cylindrical depressions 21 have a circular groove on their inner surface while the cylindrical lugs 34 have a circular groove on their outer surface.
  • a fastener washer 36 for example a circlip washer, is assembled on the circular groove of the cylindrical lug 34 prior to its introduction into the cylindrical recess 21.
  • connection between the sphere 32 of the attachment stud 33 is possible.
  • the sphere 32 could be welded, mounted tightly or still stuck directly on the plate, in place of the cylindrical lugs 34 and cylindrical depressions 21.
  • the pistons 3 may have spherical piston heads and the plate may have machined housings shaped truncated sphere.
  • the male and female parts can be reversed.
  • the heads of the pistons 3 can be held in contact with the plate 2 via a return plate associated with a ball joint.
  • the return of the piston 3 is effected by means of the return plate which holds the piston head 3 with a piston pad placed on the plate 3.
  • the return plate is pressed against the plate 2 by a ball joint.
  • variable displacement pump An example of a variable displacement pump is shown with reference to the figure 7 . Elements having the same function as those represented by reference to Figures 1 to 6 are designated by the same reference numbers.
  • a variable displacement pump is variable flow.
  • the flow rate can be adjusted for example by having means for varying the relative inclination between the plate 2 against which the pistons are supported and the axis of the pistons, so as to vary the stroke of the latter.
  • the drive shaft 1 drives the plate 2.
  • the barrel 5 is rotatably mounted and held against a dispensing window 22.
  • the barrel 5 is further centered about its axis by a guide 77 of variable orientation.
  • the angle formed between the axis of the cylinder 5 and that of the plate 2 varies via a control cylinder 27 which is supplied by a distributor.
  • the guide 77 is connected to a connecting rod 60 sliding in a plane substantially perpendicular to the axis of the barrel 5.
  • a plate 40 connected to the connecting rod 60 slides on a cradle shaped hollow cylinder according to the stroke of the control cylinder 27 and allows the variation of the displacement of the engine.
  • the pistons 3 are in connection with the plate 2.
  • the heads of the pistons 3 are held in contact with the plate 2 via a return plate 111.
  • the heads of the pistons 3 are spherical and the plate 2 has machined housings of truncated spherical shape, the return plate 111 maintaining the connection between the heads of the pistons 3 and the machined housing.
  • the pump comprises two annular seals 29 and 30 mounted on the drive shaft 1 between each of the bearings 20.
  • the annular seal 29 is mounted on the side of the drive shaft 1 intended to be in engagement with the power take-off.
  • the annular seal 30 is mounted on the side of the drive shaft 1 which is in contact with the plate 2.
  • Silicone grease is disposed between the two annular seals 29 and 30, and a tube 37 of the hydraulic leak sensor 28 is slid between the first annular seal 29 and the second annular seal 30.
  • the hydraulic leak sensor 28 further includes a 38 level connected to the tube 37 and connected to an electronic alarm 39.
  • the level 38 comprises a float and a proximity detector.
  • the hydraulic leak sensor 28 is configured to detect the presence of fluid between the two annular seals 29 and 30.
  • the hydraulic pump comprises a hydraulic chamber 31 in which are the cylinder 5 and the pistons 3.
  • the hydraulic chamber 31 is filled with hydraulic fluid when the pump is in operation.
  • the suctioned and discharged fluid can be introduced around the plate 2 and at the level of the bearing 20 on the side of the plate 2.
  • the two annular seals 29 and 30 serve as hydraulic insulation between the hydraulic chamber 31 and the side of the drive shaft 1 which is intended to be engaged with the power take-off.
  • the gearbox oil or the hydraulic fluid can be introduced between the two annular seals 29 and 30 in the event of failure of the annular seals.
  • the risk is that the hydraulic fluid enters the gearbox and drowns the engine or that the absence of hydraulic fluid is influencing the hydraulic pump.
  • the hydraulic leakage sensor 28 makes it possible immediately to identify any oil leakage from the gearbox or hydraulic fluid.
  • the hydraulic leak sensor is configured to emit a signal in response to the detection of fluid leakage between the two annular seals 29 and 30.
  • the signal is a light signal or an electronic signal, for example a signal sent on the vehicle control dial or on an application capable of displaying an alert on a device of the user, for example on a smartphone.
EP18212153.3A 2017-12-14 2018-12-13 Hydraulische pumpe mit gefassten federkugeln Withdrawn EP3499033A1 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
FR1762115A FR3075277B1 (fr) 2017-12-14 2017-12-14 Pompe hydraulique a spheres serties

Publications (1)

Publication Number Publication Date
EP3499033A1 true EP3499033A1 (de) 2019-06-19

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP18212153.3A Withdrawn EP3499033A1 (de) 2017-12-14 2018-12-13 Hydraulische pumpe mit gefassten federkugeln

Country Status (2)

Country Link
EP (1) EP3499033A1 (de)
FR (1) FR3075277B1 (de)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2023156266A1 (fr) * 2022-02-18 2023-08-24 Hydro Leduc Machine tournante hydraulique

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1993023670A1 (de) * 1992-05-14 1993-11-25 Hydromatik Gmbh Hydrostatische maschine mit leckölabführung
FR2692008A1 (fr) 1992-06-05 1993-12-10 Leduc Rene Hydro Sa Perfectionnement aux pompes hydrauliques à pistons munis de clapets d'aspiration.
US5490446A (en) * 1994-03-22 1996-02-13 Caterpillar Inc. Apparatus and method for a piston assembly
WO2005026542A1 (fr) * 2003-09-09 2005-03-24 Hydro Leduc Pompes hydrauliques a barillet tournant a double sens de rotation
DE102013209492A1 (de) * 2013-05-22 2014-11-27 Robert Bosch Gmbh Schrägscheibenmaschine
FR3012181A1 (fr) 2013-10-22 2015-04-24 Hydro Leduc Pompe hydraulique a pistons a distribution par glace bi-directionnelle
DE102016103257A1 (de) * 2016-02-24 2017-08-24 Linde Hydraulics Gmbh & Co. Kg Gleitschuh einer hydrostatischen Verdrängermaschine

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1993023670A1 (de) * 1992-05-14 1993-11-25 Hydromatik Gmbh Hydrostatische maschine mit leckölabführung
FR2692008A1 (fr) 1992-06-05 1993-12-10 Leduc Rene Hydro Sa Perfectionnement aux pompes hydrauliques à pistons munis de clapets d'aspiration.
US5490446A (en) * 1994-03-22 1996-02-13 Caterpillar Inc. Apparatus and method for a piston assembly
WO2005026542A1 (fr) * 2003-09-09 2005-03-24 Hydro Leduc Pompes hydrauliques a barillet tournant a double sens de rotation
DE102013209492A1 (de) * 2013-05-22 2014-11-27 Robert Bosch Gmbh Schrägscheibenmaschine
FR3012181A1 (fr) 2013-10-22 2015-04-24 Hydro Leduc Pompe hydraulique a pistons a distribution par glace bi-directionnelle
DE102016103257A1 (de) * 2016-02-24 2017-08-24 Linde Hydraulics Gmbh & Co. Kg Gleitschuh einer hydrostatischen Verdrängermaschine

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2023156266A1 (fr) * 2022-02-18 2023-08-24 Hydro Leduc Machine tournante hydraulique
FR3132934A1 (fr) * 2022-02-18 2023-08-25 Hydro Leduc Machine tournante hydraulique

Also Published As

Publication number Publication date
FR3075277A1 (fr) 2019-06-21
FR3075277B1 (fr) 2021-10-08

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