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
  • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
  • F04B1/10—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement the cylinders being movable, e.g. rotary
  • F04B1/107—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement the cylinders being movable, e.g. rotary with actuating or actuated elements at the outer ends of the cylinders
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
  • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
  • F01B13/00—Reciprocating-piston machines or engines with rotating cylinders in order to obtain the reciprocating-piston motion
  • F01B13/04—Reciprocating-piston machines or engines with rotating cylinders in order to obtain the reciprocating-piston motion with more than one cylinder
  • F01B13/06—Reciprocating-piston machines or engines with rotating cylinders in order to obtain the reciprocating-piston motion with more than one cylinder in star arrangement
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
  • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
  • F01B13/00—Reciprocating-piston machines or engines with rotating cylinders in order to obtain the reciprocating-piston motion
  • F01B13/04—Reciprocating-piston machines or engines with rotating cylinders in order to obtain the reciprocating-piston motion with more than one cylinder
  • F01B13/06—Reciprocating-piston machines or engines with rotating cylinders in order to obtain the reciprocating-piston motion with more than one cylinder in star arrangement
  • F01B13/061—Reciprocating-piston machines or engines with rotating cylinders in order to obtain the reciprocating-piston motion with more than one cylinder in star arrangement the connection of the pistons with the actuated or actuating element being at the outer ends of the cylinders
• • 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
  • F04B1/10—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement the cylinders being movable, e.g. rotary
• • 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
  • F04B1/10—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement the cylinders being movable, e.g. rotary
  • F04B1/107—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement the cylinders being movable, e.g. rotary with actuating or actuated elements at the outer ends of the cylinders
  • F04B1/1071—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement the cylinders being movable, e.g. rotary with actuating or actuated elements at the outer ends of the cylinders with rotary cylinder blocks

Definitions

• the invention relates to the field of mechanics and hydraulics and particularly relates to a hydrostatic machine.
• Hydrostatic machines generally have one end connected to a frame and another end connected to a rotating drive element such as a wheel, propeller or any transmission device.
• Such a hydrostatic machine can be used as a hydraulic motor. It is then supplied with pressurized hydraulic fluid and drives the rotating drive element in response.
• the hydrostatic machine can also be used as a hydraulic pump. It then receives a torque transmitted by the rotating drive element and compresses the hydraulic fluid in response.
• Patent application FR3030381 describes a hydraulic motor comprising:
• stator provided with fixings for a frame and comprising a circumferential cam path
• a rotor provided with fixings for a rotating drive element and comprising pistons distributed circumferentially and adapted to cooperate with the cam track;
• a hydraulic distributor adapted to selectively supply the pistons with hydraulic fluid so that the cooperation of the pistons with the cam path corresponds to a relative rotation of the rotor relative to the stator.
• the object of the invention is to improve this type of machine from the point of view of compactness, robustness, and the manufacturing process.
• the invention relates to a hydrostatic machine comprising:
• stator provided with fixings for a frame and comprising a circumferential cam path
• rotor provided with fixings for a rotary drive element and comprising pistons distributed circumferentially and adapted to cooperate with the cam track
• a hydraulic distributor adapted to selectively supply the pistons with hydraulic fluid so that the cooperation of the pistons with the cam path corresponds to a relative rotation of the rotor relative to the stator.
• the stator has an internal cylindrical surface of constant diameter as well as a cam ring which comprises, on its internal circumference, the cam path, and which is mounted, by its external circumference, in the internal cylindrical surface;
• Another object of the invention relates to a process for manufacturing a hydrostatic machine comprising the following steps:
• Such a hydrostatic machine has an increased compactness, which is particularly advantageous when the hydrostatic machine is intended to take place in the wheel of a vehicle to motorize the latter. In the latter case, the more compact the hydrostatic machine, the more it is able to fit in the rim of the vehicle.
• the hydrostatic machine On the internal cylindrical surface of the stator are mounted both the pivot connection elements with the rotor (the bearings) and the rotation drive elements of the rotor (the cam ring). No device or complex geometrical arrangement is necessary for the axial maintenance of these elements, the cylindrical surface being of constant diameter.
• a shoulder can be provided on the stator at the end of this internal cylindrical surface and is sufficient for positioning both the bearings and the cam ring in the stator.
• the cam ring can then combine its support function for the cam track with a positioning spacer function between the two bearings, which contributes to the axial compactness of the machine.
• the axial compactness of the machine can be further improved by providing on the cam ring an annular base allowing positioning against the outer rings of the bearings, by escaping the bearing cages as tightly as possible, without therefore hampering the rotation of the latter.
• the stator comprises a tubular casing, which promotes radial compactness.
• the internal cylindrical surface of the rotor is then supported by a thin wall in comparison with the other dimensions of the machine.
• the cam track being carried by a part (the cam ring) distinct from the rest of the stator, the function of cooperation with the pistons is decoupled from the function of structural maintenance of the elements linked to the stator.
• the cam track must have a high hardness and a high resistance to wear caused by the rolling of the pistons on the cam track. These properties are generally provided by fragile materials, such as hardened steel.
• the cam ring is therefore advantageously made of such a material because its only dynamic function is to cooperate with the pistons.
• the tubular casing performs the structural maintenance function of the elements contained in the stator and must on the contrary have a certain ductility so as not to break or crack under the effect of shocks or possible deformations during operation of the machine which is supplied by a hydraulic fluid under high pressure.
• These properties are provided to the stator by the choice of a ductile material, and of a thin thickness for the wall of the stator which can thus work in bending.
• Working in bending is favored, at least in the portion of the stator close to the internal cylindrical surface, by the fact that the stator does not require, in this portion, geometric shapes or functional excess thicknesses which would be intended for positioning elements or stiffening.
• the cam track is generally machined in the body of the stator and a heat treatment of hardening by surface quenching is provided in addition.
• a stator is difficult and expensive to produce.
• the cam ring can be made from a grade of steel called “bearing steel”, or “carbon steel”, which has a large proportion of carbon, a high resistance wear and fatigue, but which is sensitive to shocks.
• the weakness of the cam ring with respect to shocks is compensated for by its mounting in the tubular casing of the rotor, which is ductile.
• the invention thus makes it possible to benefit from the high performance of a material resistant to contact pressure and to fatigue for the production of the cam track without suffering from the drawbacks normally associated with this type of material.
• This arrangement also makes it possible to considerably simplify the manufacturing process of the hydrostatic machine.
• a main body of the rotor can be previously fitted with two bearings and the cam ring, the two bearings framing the cam ring on either side while holding it axially.
• This sub-assembly consisting of the main body of the rotor, the bearings, and the cam ring can then be, in a single operation, mounted inside the stator so that the two bearings and the cam ring are slid along the internal cylindrical surface. The assembly operations are therefore considerably simplified.
• stator production operations are also reduced by the presence of the stator tubular casing, which can be produced from a steel tube requiring little or no machining operations.
• the cam ring can be produced by machining a steel tube for bearings which is inexpensive because it is produced in large volumes for the manufacture of bearings and which has excellent properties of hardness and resistance to contact fatigue.
• the hydrostatic machine can also have the following additional characteristics, alone or in combination:
• the hydrostatic machine comprises a tubular casing, the internal cylindrical surface being defined by the tubular casing;
• the cam ring has a ductility lower than that of the tubular casing;
• the cam ring is made of steel for bearings and the tubular casing is made of non-alloy steel or austenitic stainless steel;
• the machine has anti-rotation fixings to couple the cam ring and the stator;
• the machine comprises: a clamping ring disposed axially against one of the bearings and against the rotor; a lip seal disposed between the clamping ring and the stator;
• the clamping ring is fixed to the rotor by a hub screwed into the rotor and carrying the fixings for a rotary drive element;
• the fasteners for a rotating drive element consist of screws, the heads of which are clamped by the hub.
• FIG. 2 is a perspective view showing the machine of Figure 1, on the rotor side;
• FIG. 3 is a front view along the section AA of Figure 1;
• FIG. 4 is a side view along section BB of Figure 3;
• FIG. 5 is a diagram illustrating the manufacturing process of the machine of Figures 1 to 4;
• FIG. 6 shows, in section, a sub-assembly for the production of the machine of Figures 1 to 4;
• FIG. 7 shows in perspective the tubular casing of the machine of Figure 1;
• Figure 8 shows in perspective the cam ring of the machine of Figure 1.
• Figures 1 and 2 show a hydrostatic machine 1 according to the invention, respectively side view and perspective view of the rotor side.
• the hydrostatic machine 1 has a generally cylindrical shape and comprises a stator 2 as well as a rotor 3. A relative rotational movement is allowed between the stator 2 and the rotor 3, around an axis X.
• the generally cylindrical shape is suitable to the internal constitution of the machine and allows it to be mounted, at least partially, in a cylindrical element relating to the rotating drive element, for example in the rim of a wheel.
• the hydrostatic machine 1 is intended to be fixed to a frame constituted by the chassis of a vehicle (not shown).
• a wheel (not shown) is mounted on the rotor of the machine so that the vehicle can be propelled by the rotation of the wheel.
• the hydrostatic machine 1 comprises, on the frame side (on the left of FIG. 1), means of attachment 15 to the frame as well as means 16 for supplying hydraulic fluid for the power supply of the hydrostatic machine 1.
• the hydrostatic machine 1 On the wheel side (on the right side in FIG. 1), the hydrostatic machine 1 has a hub 4 which is part of the rotor 3.
• This hub 4 has fixing means for a rotating drive element.
• the rotary drive element is a vehicle wheel (not shown) and the fixing means are studs 5 for fixing the vehicle wheel.
• the hydrostatic machine 1 thus being fixed on a frame by its stator 2, and being attached to a vehicle wheel by its rotor 3, can operate in two modes:
• FIG. 2 shows the fixing holes of the hub 4 on the rest of the rotor 3.
• FIG. 3 is a view along the section AA of FIG. 1 and illustrates the operating principle of the hydrostatic machine 1.
• the part of the rotor 3 which is visible in this FIG. 3 is its main body 31. It is a circular part in which eight radial cylinders 6 are drilled, distributed circumferentially on the main body 31 of the rotor 3.
• a hydraulic fluid supply outlet 7 opens into each of these cylinders 6.
• a piston 8 is inserted into each cylinder 6 so that the pressurization of the hydraulic fluid by the supply mouth 7 causes the piston 8 to exit radially outwards and, conversely, the movement of the piston 8 when it is constrained radially inwardly causes the hydraulic fluid to exit through the supply mouth 7 (to simplify the figure, only three pistons have been shown in FIG. 3).
• Each piston 8 is provided with a roller 9 mounted movably on the piston 8 relative to an axis parallel to the axis X.
• FIG. 3 Furthermore, two elements of the stator 2 are visible in FIG. 3: a tubular casing 10 and a cam ring 11.
• the cam ring 11 is mounted in the tubular casing 10 and these elements are made integral. Anti-rotation fasteners allow the cam ring 11 and the tubular casing to be integral in rotation.
• the anti-rotation fasteners include holes 12 distributed over the circumference of the tubular casing 10, and corresponding holes 13 made in the cam ring 11, as well as screws (not shown) for fixing.
• the cam ring 11 has on its internal circumference a cam path 14 corrugated in a succession of hollows and bumps. During the operation of the machine 1, the rollers 9 of the pistons 8 roll on the cam track 14.
• the cam ring 11 is made of bearing steel, for example 100Cr6 steel.
• the cam ring 11 is advantageously mounted tight in the tubular casing 10.
• the tubular casing 10 is made of a more ductile material than the cam ring 11. The tightening of the cam ring 11 in the tubular casing 10 makes it possible to maintain the cam ring 11 in compression in the tubular casing 10, which contributes to preventing the appearance of fatigue cracks in the cam ring 1 1.
• the pistons 8 are selectively supplied with pressurized fluid as a function of their angular position relative to the cam track 14 so that the pressure of the fluid is transformed into rotation of the cam track 14, and therefore of the rotor 3.
• FIG. 4 is a sectional view of the hydrostatic machine 1 according to section BB of FIG. 3.
• the stator 2 is made in two parts: a base 18 and a tubular casing 10.
• FIG. 4 shows, on the frame side, the means for fixing the hydrostatic machine 1 to the frame of the vehicle. In the present example, these are threaded bores 15 regularly distributed over the circumference of the tubular casing 10 and allowing its fixing by screws to the frame (not shown).
• the stator 2 also comprises, on the frame side, hydraulic connections 16 intended for the connection of the conduits of the hydraulic circuit of the vehicle for the supply of hydraulic fluid to the machine 1.
• hydraulic connections 16 are arranged on the base 18 and are connected, by internal channels of the stator 2, to a hydraulic distributor 17.
• the hydraulic distributor 17 is itself provided with internal conduits allowing the selective supply of hydraulic fluid to the pistons 8.
• the tubular casing 10 is a tube fitted on the base 18. In the present example, it is a force fitting which makes it possible to make the base 18 and the tubular casing 10 integral without any other additional fixing. Alternatively, screws or any other fixing means may be provided to consolidate the assembly.
• the tubular casing 10 has a reinforcing shoulder 19.
• the threaded bores 15 for fixing the machine 1 to the frame are here formed at the level of this reinforcing shoulder 19.
• the tubular casing 10 extends, in the direction of the wheel side, along a first shoulder 20, an internal cylindrical surface 21 of constant diameter, and a second shoulder 22, these elements being arranged in step, that is to say that the internal diameters defined respectively by the first shoulder 22, the internal cylindrical surface 21, and the second shoulder, increase in the direction of the wheel side.
• the tubular casing 10 therefore has three internal diameters, the larger is located on the wheel side.
• On the internal cylindrical surface 21 are mounted:
• the cam ring 11 has an annular base 41 for mounting in the tubular casing 10.
• the base 41 is clamped between the outer rings of the two bearings 23, 24.
• the bearings are here made of bearing steel, for example 100Cr6 steel.
• the outer rings of the bearings 23, 24 and the cam ring 11 are therefore of the same material (steel 100Cr6), preferably quenched in the mass.
• the rotor 3 is mounted rotating inside the tubular casing 10 thanks to the bearings 23, 24 which cooperate with the main body 31 of the rotor 3.
• the internal ring of the first bearing 23 is mounted on the rotor 3 so that it comes axially in abutment against a shoulder 25 of the rotor 3, this shoulder 25 being located on the frame side.
• the second bearing 24 is mounted on the rotor 3, on the wheel side, so that the two bearings 23, 24 come from either side of each cylinder 6.
• the end of the main body 31 which is on the wheel side, has a radial face 26 which coincides with the rim of the inner ring of the second bearing 24.
• the dimensions of the main body 31, of the bearings 23, 24, and of the ring cam 11, are chosen so that the chain of dimensions between the shoulder 25 and the rim of the inner ring of the second bearing 24 leads to an alignment in the same plane of the radial face 26 and of the rim of the inner ring of the second bearing 24.
• an axial end of the inner ring of the second bearing 24 is placed in the same plane as the radial face 26 of the main body 31.
• the rotor 3 further comprises a clamping ring 29 which abuts axially both against the internal ring of the second bearing 24 and against the radial face 26.
• a clamping ring 29 which abuts axially both against the internal ring of the second bearing 24 and against the radial face 26.
• the rotor 3 also comprises the wheel hub 4 which is fixed against the radial face 26 of the main body 31 by the screws 32.
• the wheel hub 4 has a shoulder 33 whose axial dimension is equal to the axial dimension of the ring. tightening 29.
• the rotor further comprises an O-ring 34 disposed in a groove in the main body 31 and interposed between the latter and the clamping ring 29 to seal between these two elements.
• a lip seal 35 is interposed between the clamping ring 29 and the tubular casing 10.
• the lip seal 35 axially abuts against the second shoulder 22.
• the O-ring 34 and the lip seal 35 jointly constitute an outward sealing barrier confining, inside the tubular casing 10, the hydraulic fluid which could be there.
• the lip seal 35 can come into abutment directly on the bearing 24 while staying away from the bearing cage of the bearing 24.
• the wheel hub 4 includes, as also visible in FIG. 2, threaded holes 36 for mounting the studs 5.
• the studs 5 are constituted by screws having a head 38 which is for example a hexagonal head dig.
• Each threaded hole 36 is associated with a counterbore 37 whose axial dimension is equal to the height of the corresponding head 38.
• the head 38 of the screws constituting the studs 5 is therefore locked in the two axial directions: by the counterbore 37 on the right side (with reference to FIG. 4) and by the clamping ring 29 on the left side (the right and left sides are indicated in reference to figure 4).
• the height of the head 38 and the axial dimension of the counterbore 37 are therefore chosen so that the studs 5 are indessible in normal operation.
• a dust-resistant annular seal 39 can also be provided between the wheel hub 4 and the tubular casing 10.
• the seal 39 has a groove 42 equipped with an axial stop.
• the threaded bores 15 which allow the hydrostatic machine 1 to be fixed to a chassis are made in the tubular casing 10 so that the forces are transmitted by a short mechanical path between the rotor and the chassis, this path passing only through the bearings 23 , 24 and the tubular casing 10.
• FIG. 5 shows the main steps of the manufacturing process.
• the base 18, the tubular casing 10 and the distributor 17, are respectively produced during steps E1, E2, E3.
• the base 18 and the distributor 17 are produced by any conventional mechanical manufacturing means, for example by molding and machining of the functional parts.
• the tubular casing 10 is advantageously produced from a rolled steel tube of type E470 (according to the European standard for the designation of steels E10027) which has the advantage of being inexpensive and having sufficient ductility for work of the tubular casing 10.
• the tubular casing 10 is thus advantageously made of a weldable steel for, optionally, welding there any external fixing required for mounting the hydrostatic machine 1.
• this E470 steel tube is equal to the thickness provided for the reinforcement shoulder 19, this tube then being machined on its internal surface to form the first shoulder 20, the internal cylindrical surface 21 and the second shoulder 22.
• the holes 12 for fixing the cam ring are finally drilled in the tubular casing 10.
• the tubular casing 10 produced in step E2 is shown in FIG. 7.
• step E6 the base 18 and the tubular casing 10 are assembled by force fitting then the hydraulic distributor 17 is put in place on the base 18.
• the main body 31 and the cam ring 11 are produced in steps E4 and E5 respectively.
• the main body 31 is also produced by any conventional mechanical means.
• the cam ring 11 is advantageously produced from a steel tube for bearings, for example 100Cr6 steel (according to the European standard for designation of steels E10027), the external diameter of which is substantially equal to the diameter of the internal cylindrical surface 21 of the tubular casing 10, according to the desired adjustment for the cam ring 11 in the tubular casing 10.
• a slice of such a steel tube for bearings is all first cut, of a dimension equal to the axial dimension provided for the base 41 of the cam ring 11. A ring is thus obtained, and the internal surface of this ring is then machined with a digital milling machine to obtain the cam path 14 visible in Figure 3.
• the base 41 is intended to be clamped between the outer rings two two bearings 23, 24 and the lateral clearances allow the passage of bearing cages which protrude axially from the inner ring.
• the base 41 is therefore rectified after the machining of the lateral clearances (which also make it possible to have less material to be rectified).
• the main body 31, the cam ring 11, and the two bearings 23, 24 are assembled to obtain the sub-assembly shown in FIG. 5.
• the first bearing 23 is first mounted around of the main body 31 until it abuts against the shoulder 25.
• the internal ring of the first bearing 23 (as well as the internal ring of the second bearing 24) can be assembled with a slight tightening on the main body 31.
• the cam ring 1 1 is then mounted around the main body 31 so as to abut against the first bearing 23. More specifically, the base 41 comes into contact with the outer ring of the first bearing 23.
• the cam ring 1 1 has, in this position, no radial support for its internal surface (the cam track 14) and must therefore be positioned so that its external surface is aligned with the external surface of the first bearing 23.
• the second bearing 24 is then in turn mounted around the main body 31 until its outer ring abuts against the base 41 of the cam ring 1 1.
• the dimensions of these various elements are chosen so that, at the end of assembly of the sub-assembly, the rim of the internal ring of the second bearing 24 coincides with the radial face 26.
• the cam ring 1 1 is also positioned axially by the bearings 23, 24.
• the sub-assembly of FIG. 5 is inserted in a single operation into the tubular casing 10 until the outer ring of the first bearing 23 comes into abutment against the first shoulder 20 of the tubular casing 10
• the cam ring 1 1 is advantageously mounted tight in the tubular casing 10, with a tightening for example from 0.01 to 0.05 mm.
• the bearings 23, 24 can also be mounted in the tubular casing 10 with a slight tightening.
• the sub-assembly of FIG. 5 can be mounted in the tubular casing 10, for example with a press, by pushing the assembly with a tubular mounting tool whose external diameter is slightly less than the diameter of the internal cylindrical surface 21 and whose thickness is small enough to interact only with the outer ring of the second bearing 24.
• This assembly is therefore carried out in a single operation of simple mechanics.
• the clamping ring and the lip seal 35 are jointly placed in the tubular casing 10 until the lip seal 35 comes into abutment axially against the second shoulder 22 of the tubular casing 10.
• the clamping ring 29 is then positioned by the lip seal 35.
• step E10 the wheel hub 4, fitted with studs 5 in place, is screwed against the main body 31 thus clamping the clamping ring 29 and the dust-proof annular seal 39 is finally put in place.
• the cam ring 11 is made of 100Cr6 steel, as are the two bearings 23, 24.
• the tubular casing 10 by its tubular shape and the material which constitutes it, has the mechanical behavior of a tube, in particular as regards the bending of its walls.
• the tubular casing 10 can bulge if it is locally deformed towards the outside by the cam ring 11, or on the contrary, it can become concave if the cam ring 11 is mechanically stressed inwards.
• the hydrostatic machine 1 has an increased longevity thanks to the damping of deformations and shocks that the tubular casing 10 achieves on the cam ring 11.
• the increased longevity is also due to the presence of a large amount of carbon in the bearing steel used for the cam ring 11, which contributes to a very low oxygen content of this steel.
• the wheel hub 4 can be dismantled, for example to change or repair the studs 5. Such an operation is here carried out simply by unscrewing the screws 32 and by extracting the wheel hub 4 without the interior of the hydrostatic machine 1 being open, that is to say without any seal being removed.
• the interior of the machine 1 thus remains sealed, making the removal and fitting operation of the wheel hub 4 simple and clean and of low criticality.
• Other alternative embodiments of the hydrostatic machine 1 can be implemented without departing from the scope of the invention.
• the materials used for the cam ring 11 and the tubular casing 10 can be other than those mentioned in the example described, from the moment when the material of the tubular casing 10 has a higher ductility than the cam ring 11.
• the hydrostatic machine can be fixed on a frame other than that of a vehicle, for example a stationary machine, and the rotary drive element can be another element than a wheel, for example a gearbox. , a machine element or any other transmission device or element to be motorized.
• the tubular casing 10 can also be produced from a stainless steel tube which will advantageously be non-martensitic to have sufficient ductility for the work of the tubular casing 10, and in any event a ductility greater than the cam 11.
• the stainless steel will be austenitic, for example an iron-chromium-nickel alloy with less than 0.1% carbon, such than "18/10" stainless steel.
• the hub 4 can also be made of stainless steel, which allows the hydrostatic machine to have an exterior entirely made of stainless steel and which allows the hydrostatic machine to be used in corrosive environments such as water. sea or corrosive chemicals.
• the tubular casing 10 and the hub 4 can both be made of another material which would be suitable for a particular application.

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• Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• General Engineering & Computer Science (AREA)
• Hydraulic Motors (AREA)
• Reciprocating Pumps (AREA)
• Valve-Gear Or Valve Arrangements (AREA)

Applications Claiming Priority (2)

Publications (2)

Family

ID=66867180

Family Applications (1)

Country Status (4)

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Family Cites Families (21)

• 2018
  • 2018-07-03 FR FR1856142A patent/FR3083573B1/fr not_active Expired - Fee Related
• 2019
  • 2019-07-03 EP EP19758791.8A patent/EP3818266B1/de active Active
  • 2019-07-03 WO PCT/FR2019/051648 patent/WO2020008145A1/fr unknown
  • 2019-07-03 US US17/257,512 patent/US11841009B2/en active Active
• 2023
  • 2023-08-29 US US18/457,459 patent/US20230400015A1/en active Pending

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