EP3818266B1 - Hydrostatische maschine mit einem nockenring - Google Patents

Hydrostatische maschine mit einem nockenring Download PDF

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Publication number
EP3818266B1
EP3818266B1 EP19758791.8A EP19758791A EP3818266B1 EP 3818266 B1 EP3818266 B1 EP 3818266B1 EP 19758791 A EP19758791 A EP 19758791A EP 3818266 B1 EP3818266 B1 EP 3818266B1
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EP
European Patent Office
Prior art keywords
cam ring
stator
rotor
hydrostatic machine
tubular casing
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EP19758791.8A
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English (en)
French (fr)
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EP3818266A1 (de
Inventor
Laurent Eugène ALBERT
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Individual
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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
    • F04B1/04—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
    • 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
    • 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, a propeller or any transmission device.
  • Such a hydrostatic machine can be used as a hydraulic motor. It is then fed by a 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 in response compresses the hydraulic fluid.
  • the object of the invention is to improve this type of machine from the point of view of compactness, robustness, and the manufacturing process.
  • Such a hydrostatic machine has 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 into the wheel rim of the vehicle.
  • a shoulder can be provided on the stator at the end of this internal cylindrical surface and is sufficient for positioning both the two 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 axial compactness. of the machine.
  • the axial compactness of the machine can be further improved by providing an annular base on the cam ring allowing positioning against the outer rings of the bearings, by escaping the bearing cages as tightly as possible, without therefore interfering with their rotation.
  • 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 for its part, carries out the function of structural maintenance 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 fed by hydraulic fluid under high pressure.
  • These properties are provided to the stator by the choice of a ductile material, and a thin thickness for the wall of the stator which can thus work in bending.
  • the bending work 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 extra thicknesses which would be intended for positioning. of elements or stiffening.
  • the cam track is generally machined in the body of the stator and a hardening heat treatment 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 high proportion of carbon, a high resistance to wear and fatigue, but which is nevertheless sensitive to shocks.
  • bearing steel or "carbon steel”
  • the weakness of the cam ring vis-à-vis shocks is compensated 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 producing the cam track without suffering from the disadvantages normally associated with this type of material.
  • This assembly also makes it possible to considerably simplify the manufacturing process of the hydrostatic machine.
  • a main body of the rotor can be equipped beforehand with the two bearings and the cam ring, the two bearings framing on either side the cam ring by maintaining it axially .
  • This subassembly consisting of the main body of the rotor, the bearings, and the cam ring can then, in a single operation, be mounted inside the stator so that the two bearings and the cam ring are slid along the along the inner cylindrical surface. Assembly operations are therefore considerably simplified.
  • stator casing which can be produced from a steel tube requiring little or no machining operations.
  • the cam ring can be made 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 figures 1 and 2 represent a hydrostatic machine 1 according to the invention, respectively side view and perspective view from 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 permitted between the stator 2 and the rotor 3, around an axis X.
  • the generally cylindrical shape is adapted to the internal structure 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 on a frame consisting of 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 the figure 1 ), fastening means 15 to the frame as well as hydraulic fluid supply means 16 for supplying power to the hydrostatic machine 1.
  • the hydrostatic machine 1 On the wheel side (on the right side on the figure 1 ), the hydrostatic machine 1 comprises a hub 4 which forms part of the rotor 3.
  • This hub 4 comprises fastening means for a rotating drive element.
  • the rotating drive element is a vehicle wheel (not shown) and the fixing means are studs 5 for fixing the vehicle wheel.
  • the picture 2 shows the fixing holes of the hub 4 on the rest of the rotor 3.
  • the picture 3 is a view according to section AA of the figure 1 and illustrates the principle of operation of the hydrostatic machine 1.
  • the part of rotor 3 which is visible on this picture 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 mouth 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 inwards causes the hydraulic fluid to exit through the supply mouth 7 (to simplify the figure, only three pistons have been shown on the picture 3 ).
  • Each piston 8 is provided with a roller 9 mounted to move on the piston 8 with respect to an axis parallel to the axis X.
  • stator 2 two elements of the stator 2 are visible on the picture 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 fixings allow the cam ring 11 and the tubular casing to be integral in rotation.
  • the anti-rotation fixings comprise 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) to ensure the fixing.
  • the cam ring 11 has on its inner circumference a cam path 14 corrugated in a succession of hollows and bumps. During 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 helps to prevent the occurrence of fatigue cracks in the cam ring 11.
  • the pistons 8 are selectively supplied with fluid under pressure according to 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.
  • the figure 4 is a sectional view of the hydrostatic machine 1 according to section BB of the picture 3 .
  • the stator 2 is made in two parts: a base 18 and a tubular casing 10.
  • the figure 4 shows, on the frame side, the means for fixing the hydrostatic machine 1 to the frame of the vehicle.
  • 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 connectors 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 connectors 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 ducts allowing the selective supply of hydraulic fluid to the plungers 8.
  • the tubular casing 10 is a tube fitted onto the base 18. In the present example, it is a force fit which makes it possible to make the base 18 and the tubular casing 10 integral without any additional fixing. As a variant, screws or any other fixing means can be provided to consolidate the assembly.
  • the tubular casing 10 comprises a reinforcing shoulder 19.
  • the threaded bores 15 for fixing the machine 1 to the frame are here made 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 Apart from the reinforcing shoulder 19, the function of which is not linked to the cooperation with the rotor 3 but only to the fixing and assembly of the stator 2, the tubular casing 10 therefore comprises three internal diameters, the larger is located on the wheel side.
  • the cam ring 11 has an annular base 41 for its 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 of 100Cr6 steel.
  • the outer rings of the bearings 23, 24 and the cam ring 11 are therefore of the same material (100Cr6 steel), preferably solid-hardened.
  • the rotor 3 is rotatably mounted inside the tubular casing 10 thanks to the bearings 23, 24 which cooperate with the main body 31 of the rotor 3.
  • the inner 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 edge of the inner race of the second bearing 24.
  • the dimensions of the main body 31, of the bearings 23, 24, and of the cam 11, are chosen so that the chain of dimensions between the shoulder 25 and the edge of the inner ring of the second bearing 24 leads to an alignment in the same plane of the radial face 26 and the edge 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 inner ring of the second bearing 24 and against the radial face 26.
  • the chain of dimensions mentioned above leads to the fact that the edge of the inner ring of the second bearing 24 is slightly axially beyond the radial face 26, so that the fixing of the clamping ring 29 leads to a preload of the bearings 23, 24.
  • 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 of tightening 29.
  • the rotor further comprises an O-ring 34 disposed in a groove of the main body 31 and interposed between the latter and the clamping ring 29 to ensure sealing between these two elements.
  • a lip seal 35 is interposed between the clamping ring 29 and the tubular casing 10.
  • the lip seal 35 abuts axially against the second shoulder 22.
  • the lip seal 35 can come directly into abutment on the bearing 24 while remaining away from the bearing cage of the bearing 24.
  • the wheel hub 4 comprises, as also visible in picture 2 , threaded holes 36 for mounting the studs 5.
  • the studs 5 consist of screws having a head 38 which is for example a hollow hexagonal head.
  • 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 blocked in the two axial directions: by the counterbore 37 on the right side (in reference to the figure 4 ) and through the clamping ring 29 on the left side (the right and left sides are indicated in reference to the figure 4 ).
  • the height of the head 38 and the axial dimension of the counterbore 37 are therefore chosen so that the studs 5 cannot be loosened in normal operation.
  • An annular dust 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 fixing of the hydrostatic machine 1 on a frame are made in the tubular casing 10 so that the forces are transmitted by a short mechanical path between the rotor and the frame, this path passing only through the bearings 23 , 24 and the tubular casing 10.
  • 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 the functional parts.
  • the tubular casing 10 is advantageously produced from a rolled steel tube of the E470 type (according to the European standard for the designation of steels E10027) which has the advantage of being inexpensive and of having sufficient ductility for the work. of the tubular casing 10.
  • the tubular casing 10 is thus advantageously made of a weldable steel in order, optionally, to weld thereto any external fixing required for mounting the hydrostatic machine 1.
  • this E470 steel tube is equal to the thickness provided for the reinforcing 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 figure 7 .
  • step E6 the base 18 and the tubular casing 10 are assembled by force fitting then the hydraulic distributor 17 is placed on the base 18.
  • the main body 31 and the cam ring 11 are manufactured respectively in steps E4 and E5.
  • 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 the designation of steels E10027), the external diameter of which is substantially equal to the diameter of the internal cylindrical surface 21 of the tubular housing 10, according to the desired fit for the cam ring 11 in the tubular housing 10.
  • a slice of such bearing steel tube is 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 the digital milling machine to obtain the cam track 14 visible at picture 3 .
  • the base 41 is intended to be clamped between the outer rings two two bearings 23, 24 and the lateral reliefs allow the passage of the bearing cages that 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 rectify).
  • the holes 13 intended for fixing in the tubular casing are then made over the entire contour of the cam ring.
  • the cam ring from operation E5 is shown in figure 8 .
  • the main body 31, the cam ring 11, and the two bearings 23, 24 are assembled to obtain the subassembly shown in figure 5 .
  • the first bearing 23 is first mounted around the main body 31 until it comes into abutment against the shoulder 25.
  • the inner ring of the first bearing 23 (like the inner ring of the second bearing 24) can be assembled with a slight tightening on the main body 31.
  • the cam ring 11 is then mounted around the main body 31 so as to come into abutment against the first bearing 23. More precisely, the base 41 comes into contact with the outer ring of the first bearing 23.
  • the cam ring 11 does not 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 comes into abutment against the base 41 of the cam ring 11.
  • the dimensions of these various elements are chosen so that, at the end of assembly of the sub-assembly, the edge of the inner ring of the second bearing 24 coincides with the radial face 26.
  • the cam ring 11 is also positioned axially by bearings 23, 24.
  • the subset of the figure 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 11 is advantageously tightly mounted in the tubular casing 10 , with a tightening for example of 0.01 to 0.05 mm.
  • the bearings 23, 24 can also be mounted in the tubular casing 10 with a slight tightening.
  • the subset of the figure 5 can be mounted in the tubular casing 10, for example using a press, by pushing the assembly with a tubular assembly tool whose external diameter is slightly smaller than the diameter of the internal cylindrical surface 21 and whose thickness is sufficiently small to interact only with the outer ring of the second bearing 24.
  • This assembly is therefore carried out in a single simple mechanical operation.
  • the clamping ring and the lip seal 35 are jointly placed in the tubular casing 10 until the lip seal 35 abuts 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, provided with studs 5 in place, is screwed against the main body 31 thus clamping the clamping ring 29 and the annular dust seal 39 is finally put in place.
  • the cam ring 11 is in this example made of 100Cr6 steel, as are the two bearings 23, 24.
  • the tubular casing 10 due to its tubular shape and the material of which it is made, has the mechanical behavior of a tube, in particular as regards the bending of its walls. In other words, the tubular casing 10 can bulge if it is locally deformed outwards by the cam ring 11, or on the contrary, it can become concave if the cam ring 11 is mechanically biased inwards.
  • the hydrostatic machine 1 has an increased longevity thanks to the damping of deformations and shocks produced by the tubular casing 10 on the cam ring 11.
  • the increased durability is also due to the presence of a significant 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 is capable of being 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 opened, that is to say without any seal being dismantled.
  • the interior of the machine 1 thus remains sealed, making the operation of removing and installing the wheel hub 4 simple and clean and of low criticality.
  • the materials used for the cam ring 11 and the tubular casing 10 may be other than those mentioned in the example described, provided that the material of the tubular casing 10 has a greater 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 rotating drive element can be an element other 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 made from a stainless steel tube which will advantageously be non-martensitic to present sufficient ductility for the work of the tubular casing 10, and in any event a greater ductility 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 moreover also be made of stainless steel, which allows the hydrostatic machine to have an exterior entirely of stainless steel and which makes it possible to use the hydrostatic machine in corrosive environments such as 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)
  • Valve-Gear Or Valve Arrangements (AREA)
  • Reciprocating Pumps (AREA)

Claims (12)

  1. Hydrostatische Maschine (1), welche aufweist:
    - einen Stator (2), der mit Befestigungselementen für ein Gestell ausgestattet ist und eine umlaufende Nockenbahn (14) aufweist;
    - einen Rotor (3), der mit Befestigungselementen für ein rotierendes Antriebselement ausgestattet ist und Kolben (8) aufweist, die über den Umfang verteilt sind und dafür eingerichtet sind, mit der Nockenbahn (14) zusammenzuwirken;
    einen hydraulischen Verteiler (17), der dafür eingerichtet ist, die Kolben (8) selektiv mit Hydraulikfluid zu versorgen, derart, dass das Zusammenwirken der Kolben (8) mit der Nockenbahn (14) einer relativen Drehung des Rotors (3) in Bezug auf den Stator (2) entspricht;
    wobei die hydrostatische Maschine (1) dadurch gekennzeichnet ist, dass:
    - der Stator (2) eine zylindrische Innenfläche (21) mit konstantem Durchmesser sowie einen Nockenring (11) aufweist, welcher auf seinem Innenumfang die Nockenbahn (14) umfasst und welcher über seinen Außenumfang in der zylindrischen Innenfläche (21) angebracht ist;
    - sie zwei Wälzlager (23, 24) aufweist, welche die Drehung des Rotors (3) in Bezug auf den Stator (2) ermöglichen und welche auf der zylindrischen Innenfläche (21) des Stators (2) axial beiderseits des Nockenringes (11) angebracht sind, wobei der Nockenring (11) und die zwei Wälzlager (23, 24) denselben Außendurchmesser aufweisen.
  2. Hydrostatische Maschine nach Anspruch 1, dadurch gekennzeichnet, dass der Stator (2) ein rohrförmiges Gehäuse (10) aufweist, wobei die zylindrische Innenfläche (21) durch das rohrförmige Gehäuse (10) definiert wird.
  3. Hydrostatische Maschine nach Anspruch 2, dadurch gekennzeichnet, dass der Nockenring (11) eine Duktilität aufweist, die geringer als diejenige des rohrförmigen Gehäuses (10) ist.
  4. Hydrostatische Maschine nach Anspruch 3, dadurch gekennzeichnet, dass der Nockenring (11) aus Wälzlagerstahl besteht, und dadurch, dass das rohrförmige Gehäuse (10) aus unlegiertem Stahl besteht.
  5. Hydrostatische Maschine nach Anspruch 3, dadurch gekennzeichnet, dass der Nockenring (11) aus Wälzlagerstahl besteht, und dadurch, dass das rohrförmige Gehäuse (10) aus austenitischem Edelstahl besteht.
  6. Hydrostatische Maschine nach Anspruch 4 oder 5, dadurch gekennzeichnet, dass das Material des Nockenringes (11) und dasjenige der zwei Wälzlager (23, 24) derselbe Wälzlagerstahl sind.
  7. Hydrostatische Maschine nach einem der Ansprüche 2 bis 5, dadurch gekennzeichnet, dass der Nockenring (11) in das rohrförmige Gehäuse (10) eingespannt montiert ist.
  8. Hydrostatische Maschine nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass sie Elemente zur verdrehsicheren Befestigung (12, 13) zum Koppeln des Nockenringes (11) und des Stators (2) aufweist.
  9. Hydrostatische Maschine nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass sie aufweist:
    - einen Spannring (29), der axial an einem (24) der Wälzlager und am Rotor (3) anliegend angeordnet ist;
    - einen Lippendichtring (35), der zwischen dem Spannring (29) und dem Stator (2) angeordnet ist.
  10. Hydrostatische Maschine nach Anspruch 9, dadurch gekennzeichnet, dass der Spannring (29) am Rotor (3) durch eine Nabe (4) befestigt ist, die in den Rotor (3) eingeschraubt ist und die Befestigungselemente (5) für ein rotierendes Antriebselement trägt.
  11. Hydrostatische Maschine nach Anspruch 10, dadurch gekennzeichnet, dass die Befestigungselemente für ein rotierendes Antriebselement aus Schrauben (5) bestehen, deren Köpfe (38) durch die Nabe (4) eingespannt sind.
  12. Verfahren zur Herstellung einer hydrostatischen Maschine (1), dadurch gekennzeichnet, dass es die folgenden Schritte umfasst:
    - Bearbeiten eines Rohres aus Wälzlagerstahl, um einen Nockenring (11) herzustellen, der eine Nockenbahn (14) aufweist;
    - Anbringen des Nockenringes (11) und zweier Wälzlager (23, 24) an einem Hauptkörper (31) eines Rotors (3), wobei der Nockenring (11) zwischen den zwei Wälzlagern (23, 24) eingespannt wird, um eine Unterbaugruppe zu bilden;
    - axiales Einsetzen der Unterbaugruppe in einen Stator (2), welcher eine zylindrische Innenfläche (21) mit konstantem Durchmesser aufweist, wobei die Wälzlager (23, 24) und der Nockenring (11) dann in der zylindrischen Innenfläche (21) angebracht werden.
EP19758791.8A 2018-07-03 2019-07-03 Hydrostatische maschine mit einem nockenring Active EP3818266B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR1856142A FR3083573B1 (fr) 2018-07-03 2018-07-03 Machine hydrostatique comportant une bague de came
PCT/FR2019/051648 WO2020008145A1 (fr) 2018-07-03 2019-07-03 Machine hydrostatique comportant une bague de came

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FR3083573B1 (fr) * 2018-07-03 2020-10-02 Laurent Eugene Albert Machine hydrostatique comportant une bague de came
JP7068410B2 (ja) * 2020-09-28 2022-05-16 大同メタル工業株式会社 ラジアルピストン機械の軸受装置
JP7167108B2 (ja) * 2020-09-28 2022-11-08 大同メタル工業株式会社 ラジアルピストン機械の軸受装置

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US20210285429A1 (en) 2021-09-16
EP3818266A1 (de) 2021-05-12
US20230400015A1 (en) 2023-12-14
FR3083573B1 (fr) 2020-10-02
FR3083573A1 (fr) 2020-01-10
WO2020008145A1 (fr) 2020-01-09
US11841009B2 (en) 2023-12-12

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