EP3406901B1 - Hydraulisches gerät, das einen verbesserten verteiler umfasst - Google Patents

Hydraulisches gerät, das einen verbesserten verteiler umfasst Download PDF

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Publication number
EP3406901B1
EP3406901B1 EP18173896.4A EP18173896A EP3406901B1 EP 3406901 B1 EP3406901 B1 EP 3406901B1 EP 18173896 A EP18173896 A EP 18173896A EP 3406901 B1 EP3406901 B1 EP 3406901B1
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EP
European Patent Office
Prior art keywords
core
distribution ring
distributor
abutment
axis
Prior art date
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Application number
EP18173896.4A
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English (en)
French (fr)
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EP3406901A1 (de
Inventor
Bertrand BONNOMET
Maxime MAURER
Stéphane Vidal
Christophe Gouzou
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.)
Poclain Hydraulics Industrie
Original Assignee
Poclain Hydraulics Industrie
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Publication of EP3406901A1 publication Critical patent/EP3406901A1/de
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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
    • F04B1/0404—Details or component parts
    • F04B1/0452—Distribution members, e.g. valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
    • F03C1/00—Reciprocating-piston liquid engines
    • F03C1/02—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders
    • F03C1/04—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinders in star or fan arrangement
    • F03C1/0403—Details, component parts specially adapted of such engines
    • F03C1/0435—Particularities relating to the distribution members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
    • F03C1/00—Reciprocating-piston liquid engines
    • F03C1/02—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders
    • F03C1/04—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinders in star or fan arrangement
    • F03C1/047—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinders in star or fan arrangement the pistons co-operating with an actuated element at the outer ends of the cylinders
    • F03C1/0472—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinders in star or fan arrangement the pistons co-operating with an actuated element at the outer ends of the cylinders with cam-actuated distribution members
    • 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
    • F04B1/047—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement with actuating or actuated elements at the outer ends of the cylinders
    • F04B1/0472—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement with actuating or actuated elements at the outer ends of the cylinders with cam-actuated distribution members

Definitions

  • This presentation concerns hydraulic devices, and more specifically distributors for hydraulic devices.
  • one of the two parts of the distributor is supported on the cylinder block of the engine, while the other part is carried by the structure of the engine.
  • the relative positioning of the two parts is limited by the support of the distributor on the cylinder block of the engine.
  • the present presentation thus aims to respond at least partially to this problem.
  • the present description relates to a distributor for a hydraulic device, comprising a core and a distribution crown mounted rotating around the core along an axis defining a proximal end and a distal end, the distribution crown and the core being mounted sliding.
  • the core having a plurality of internal grooves opening into an external periphery of the core, the distribution ring having a plurality of external grooves opening into an internal periphery of the distribution ring, said internal and external grooves being configured to be placed in fluid communication and to form fluid circulation conduits, the core comprising a plurality of sealing segments configured so as to isolate each of said fluid circulation conduits, the core having a decreasing external section from a distal end towards a proximal end, the distributor being characterized in that one of the core and the distribution crown comprises a stopper configured so as to come into contact with a wall of the other among the core and the distribution crown in order to limit the displacement of the core with respect to the distribution ring in a direction defined by the axis.
  • Said stopper is configured so as to limit the displacement along the axis of the core with respect to the distribution ring, from the distal end to the proximal end.
  • Each of said core sealing segments is positioned in a housing arranged in the core, and is in abutment against an internal face of the distribution crown, and the stop is configured so as to limit the displacement of the core relative to the crown distribution in a direction defined by the axis so that the distance between the proximal sealing segment and the proximal clearance of the distribution crown remains non-zero, the proximal sealing segment being the closest sealing segment along the axis of the proximal end of the core, and the proximal clearance of the distribution ring being defined as the first variation in section of the internal surface of the distribution ring bearing against the proximal sealing segment, towards a proximal end of the distribution ring.
  • Said stopper is typically integral with the distribution ring, and is configured so as to come into contact with a wall of the core.
  • said abutment is integral with the core, and is configured so as to come into contact with a wall of the distribution crown.
  • the present description also relates to a hydraulic device with radial pistons and multi-lobe cam, comprising a distributor as defined above, in which there is a non-zero clearance along the axis between the stop of the distributor and a surface of the core disposed opposite the stop.
  • the present disclosure also relates to a method of assembling a hydraulic device on a wheel spindle, in which a first set of components of the hydraulic device is positioned around an axis of the wheel spindle, we provide a distributor as defined above, the distributor is positioned in abutment against components of the first set of components, so as to define a non-zero clearance along an axis of the stub axle between the distributor stop and a surface of the core disposed opposite the stop, the core is secured to a component of the first set of components, a second set of components of the hydraulic device is positioned, so as to define an internal casing volume in which the distributor is positioned.
  • the figure 1 shows a hydraulic system comprising a casing 10 in which is disposed a hydraulic device 12, a shaft 14 engaged in the casing 10 and a sealing device 16 between the shaft and the casing.
  • the shaft 14 and the casing 10 are mounted so that they can rotate relative to each other about an axis A.
  • the shaft 14 is typically a spindle wheel of a vehicle, the hydraulic device 12 then typically carrying out the rotational driving of a vehicle wheel.
  • the hydraulic device 12 as shown comprises a cylinder block 12A, a cam 12B and a fluid distributor 40.
  • Cam 12B can be a multi-lobe cam. It is therefore, with the housing, a hydraulic motor or a pump.
  • This hydraulic device 12 can be in particular with radial pistons.
  • the cylinders of the cylinder block 12A are supplied with fluid from a fluid distributed by the distributor 40, via grooves which will be described later.
  • the distributor 40 is itself connected to main pipes 1 and 2, respectively for the supply and the exhaust of the hydraulic device 12.
  • the hydraulic device 12 can be of the cylinder block type 12A fixed and with casing 10 rotating, and the supply and exhaust pipes 1 and 2 pass through the shaft 14 of the wheel stub, in which they are oriented axially, that is to say parallel to the 'axis A of rotation, axis along which the shaft 14 is oriented.
  • another pipe 3 is pierced axially in the shaft 14. It is a fluid supply pipe, which serves to bring the fluid to the interior space 11 of the casing 10, in particular to put this space under pressure so as to favor the disengagement of the pistons from the hydraulic device, and to evacuate this fluid when the pistons and the cam 12B come into contact.
  • the pipe 3 makes it possible to produce a fluid in the interior space 11 of the casing so as to cause a rise in pressure therein causing a retraction of the pistons in the cylinders of the cylinder block 12A so that the pistons are not no longer in contact with the cam 12B, thus operating what is called a declutching of the hydraulic device 10 and making it possible to put the engine in freewheeling configuration.
  • a declutching of the hydraulic device 10 Conversely, the fact of bringing the pistons into contact with the cam 12B is called a dog clutch or a displacement of the hydraulic device 10.
  • the fluid supplied by the pipe 3 reaches between the opposite faces of the distributor 40 and from the shaft 14 and flows towards the interior space 11 of the casing 10, for example by a dedicated connection, or else by a clearance made on a part of the splines between the shaft 14 and the cylinder block 12A.
  • the shaft has only three axial sections of fluid pipe, namely two main sections which form all or part of the main supply and exhaust pipes 1 and 2 and an auxiliary section which forms all or part of the casing pressure line 3.
  • This auxiliary section typically forms a drain pipe for the internal volume 11 of the casing 10 when the hydraulic device 12 is in operation.
  • the cam 12B forms a part of the casing 10, which also comprises a cover 10A situated around the distributor 40 and secured to the cam 12B, typically by bolting, and a part 10B forming, for example, a flange for connection with a member driven by the motor, for example the hub of a wheel.
  • the casing 10 is extended by a part 10C, which can for example be engaged in the hub of a wheel.
  • the housing 10 and the shaft 14 are mounted in relative rotation. For this reason, they cooperate with each other via bearings 18A and 18B, housed in this case in part 10C of the casing. In known manner, these bearings 18A and 18B can be bearings with tapered bearings.
  • the system can be used for driving a vehicle wheel, in which case the shaft 14 can be a wheel spindle axle.
  • the distributor 40 comprises a distribution crown 60 and a core 50, the distribution crown 60 and the core 50 are in relative displacement in rotation.
  • the distribution ring 60 has a relative displacement in rotation relative to the cylinder block 12A, while the core 50 is secured to the shaft 14, typically by bolting.
  • the figures 2 and 3 are detailed views of the dispenser 40 shown in the figure 1 .
  • a proximal end 40P and a distal end 40D are defined for the distributor 40, the proximal end 40P being defined arbitrarily as being the end of the distributor 40 closest to the shaft 14.
  • the core 50 and for the distribution ring 60 a proximal end 50P, 60P and a distal end 60P, 60D.
  • the proximal end 50P of the core 50 forms the proximal end 40P of the distributor 40
  • the distal end 60D of the distribution crown 60 forms the distal end 40D of the distributor 40.
  • the core 50 is inserted via its proximal end 50P into the distribution ring 60 from the distal end 60D, and slides in an internal volume of the distribution ring 60 in the direction of the proximal end 60P, for example until protrusion from its proximal end 60P.
  • the core 50 thus has a decreasing external section from its distal end 50D towards its proximal end 50P, while the distribution ring 60 defines an internal housing delimited by an internal section whose section decreases from the distal end 60D towards the end proximal 60P.
  • the distributor 40 comprises supply conduits 41 and 42 arranged in the core 50, which are only primed in the figures, and which, on the one hand, open onto the radial face of the internal distributor 50 facing the shaft 14 , so as to be opposite the ends of the pipes 1 and 2 located at this end of the shaft 14 and which, on the other hand, are connected to distribution grooves arranged in the core 50 and in the distribution crown 60.
  • Distribution conduits open radially on the face forming the end proximal 60P of the distribution ring 60 so as to connect the external grooves 60A and 60B to the cylinder block 12A of the hydraulic device 12, so as to selectively supply each chamber of the cylinder block 12A of the hydraulic device 12 during its rotation.
  • the core 50 thus has internal grooves 50A and 50B opening into its external periphery, and connected to the supply conduits 41 and 42.
  • the distribution ring 60 has external grooves 60A and 60B opening into the internal periphery of the ring distribution 60, and configured so as to each be placed in fluid communication with at least one internal groove of the core 50.
  • the external grooves 60A and 60B arranged in the distribution ring 60 are connected to conduits opening on the radial face of the distribution ring 60 facing the cylinder block 12A, so as to supply and discharge fluid.
  • the communication between the main pipes 1 and 2 and the supply pipes 41 and 42 is sealed off from the rest of the system by any suitable sealing means, for example by annular seals 31 and 32 arranged between the faces opposite the core 50 and the shaft 14, or the segments, or even the compositions of joints and segments.
  • the core 50 comprises a plurality of grooves 51 in which are arranged segments 52 ensuring a sealed contact between the core 50 and the distribution ring 60, and thus making it possible to isolate the various conduits produced in the distributor 40 the relative to each other, and relative to the environment outside the gorges.
  • Each groove of the distributor 40 is therefore surrounded by segments.
  • each internal groove 50A and 50B of the core 50 is surrounded by two pairs of grooves 51 and segments 52.
  • the sealing means 52 are typically placed for mounting in the grooves 51 by stretching them to increase their diameter. Then they are placed in the grooves 51. Next, the core 50 is placed in the crown 60, and the sealing means 52 are supported on the internal wall of the crown 60. This allows movement, in particular essentially axial sliding along the axis AA between the core and crown, while obtaining the watertightness of the grooves 50A and 50B.
  • a recurring problem during the assembly of the hydraulic device is the maintenance in position of the segments 52 in the grooves 51 when the distributor 40 is handled individually, or more generally when the distributor 40 is not mounted in abutment against other components of a hydraulic device. Indeed, it is understood that if the core 50 slides in the distribution crown 60 during its manipulation to put it in position, there is a risk that segments come out of the internal volume defined by the distribution crown 60, and disengage , in particular at the level of the proximal end 50P of the core 50.
  • the distributor 40 as proposed comprises a stop 65 formed in or carried by the core 50 or by the distribution crown 60, configured so as to limit the displacement of the core relative to the distribution crown in a direction defined by the axis A.
  • a stop 65 it is understood that the distribution ring 60 may have a single stop, several similar stops arranged around the axis A, or another annular, the operation then remaining unchanged.
  • This stop 65 extends from the internal surface of the distribution ring 60, so as to come into contact with a wall of an internal groove 50A or 50B of the core 50 and thus limit the displacement of the core 50 relative to the distribution ring 60 along the axis A in a direction going from the distal end 40D towards the proximal end 40P of the distributor 40.
  • the stop 65 is typically a rib or a shoulder extending from the internal surface of the distribution ring 6.
  • the stop is typically an insert, such as a pin, inserted in an internal groove of the core 50 as will be seen below with reference to the various embodiments.
  • the stop 65 is a shoulder formed in the internal wall of the distribution ring 60, configured so as to extend in the internal groove 50B when the core 50 is inserted in the distribution crown 60.
  • the stop 65 is configured so as not to come into contact with the core 50 once the hydraulic device is assembled. More precisely, the stop 65 is thus configured so as to be able to come into contact with the core 50 only during assembly of the hydraulic device comprising the distributor 40.
  • the figure 2 is thus a detailed view of the distributor 40 shown in the figure 1
  • the figure 3 is a view of the distributor 40 taken in isolation.
  • a non-zero functional clearance J remains between the stop 65 and the surface of the core 50 opposite the stop 65, here a wall of the internal groove 50B.
  • This functional clearance results from the different contact surfaces of the core 50 and the distribution ring 60 with the other elements of the hydraulic device 12, in particular with the shaft 14 and the cylinder block 12A.
  • the core 50 is no longer limited in translation by its contact with the shaft 14.
  • the stop 65 then makes it possible to limit the displacement of the core 50 relative to the distribution ring 60 in a direction going from the distal end 60D towards the proximal end 60P of the distribution crown 60. More specifically, if we consider the position of the distributor 40 shown on the figure 2 , an additional displacement corresponding to the functional clearance J can occur when the distributor 40 is taken in isolation.
  • the stop 65 is configured so as to limit the displacement of the core 50 relative to the distribution crown 60 in order to prevent a segment 52 of the core 50 from passing beyond the proximal end 60P of the distribution crown 60, or more precisely does not come out of the timing ring 60.
  • the sealing segment 52 closest to the proximal end 50P of the core 50 is considered here.
  • the distribution ring 60 has an internal surface opposite this segment 52. This internal surface of the ring is defined for this distribution 60 a proximal clearance 63, corresponding to the first variation in section of the internal surface of the distribution ring opposite the segment 52, towards the proximal end 60P of the distribution ring 60.
  • this proximal clearance 63 thus corresponds to a section of the distribution ring 60 not necessarily ensuring that the segment 52 is maintained in its housing 51 of the core 50.
  • the stop 65 is configured so that the distance measured along the axis A between the proximal clearance 63 and the closest segment (along the axis A) of the proximal end 50P of the core 50 remains non-zero, and therefore of so that the segment 52 cannot go beyond the proximal clearance 63.
  • the segment 52 closest to the proximal end 50P of the core 50 remains held in place by the internal surface of the distribution crown 60.
  • the proximal clearance 63 corresponds to the proximal end 60P of the distribution crown 60.
  • the stop 65 is then configured so that the length (measured along the axis A) of the portion of the core 50 which may project from the proximal end 60P of the distribution crown 60 is strictly less than the distance (measured along the axis A) between the proximal end 50P of the core 50 and the segment 51 closest to said end proximal 50P of the nucleus 50.
  • the user will hold the distributor 40 by its distal end 40P in order to come to rest it against the shaft 14 and against the block 12A cylinders.
  • the user thus prevents disengagement via the distal end 40D, while the stop 65 prevents disengagement via the proximal end 40P.
  • the user can then secure the core 50 to the shaft 14, for example by bolting, which fixes the distributor 40 and then prevents any subsequent risk of falling before positioning the remaining elements of the system.
  • the segments 52 are held sandwiched between the core 50 and the distribution ring 60, which prevents any risk of loss or accidental fall of a segment.
  • the figure 4 presents a variant of the embodiment shown in figure 3 .
  • the stop 65 is here a shoulder extending from a radial wall of an external groove 60A. As for the embodiment described with reference to the figure 3 , the stop 65 comes into contact with a radial wall of an internal groove, here the internal groove 50A in order to limit the displacement of the core 50 relative to the distribution ring 60 in a direction going from the distal end 60D towards the proximal end 60P of the distribution crown 60.
  • the figure 5 shows a variant in which the stop 65 is formed by a shoulder extending from the outer periphery of the core 50 of the distributor 40.
  • This shoulder forming a stop 65 then comes into abutment against a radial surface of the distribution ring 60, in order to limit the displacement of the core 50 relative to the distribution crown 60 in a direction going from the distal end 60D towards the proximal end 60P of the distribution crown 60.
  • the shoulder as shown is formed adjacent to the internal groove 50B , it is understood that it can also be formed adjacent to the internal groove 50A, the function then being carried out identically.
  • the figure 6 shows another variant in which the stop 65 is formed at the proximal end 60P of the distribution ring 60.
  • This stop 65 thus limits the movement of the core 50, a radial wall of which comes into contact with the stop 65. Operation remains unchanged. It is noted that the stop 65 forms the proximal clearance 63, but ensures by its location that the segments cannot leave the distribution ring 60 through the proximal end.
  • the figure 7 represents another variant in which the stop 65 is formed by a screw inserted in a hole 66 formed in the distribution ring 60.
  • the hole 66 is made so that the screw forming the stop can be inserted in an internal groove, here the internal groove 50B.
  • the end of the screw entering the internal groove here defines a limited axial clearance of the core 50 relative to the distribution ring 60 in both directions of the axis A.
  • the screw can be held in position or be removed by the operator, and the hole 66 is then closed.
  • Sealing elements such as seals (not shown) are typically provided between the screw and the bore 66.
  • a functional clearance is typically provided radially between the free end of the screw forming the stop 65 and the axial wall of the groove associated.
  • the figure 8 shows another variant in which a shoulder extends from the distal end 50D of the core 50.
  • This shoulder forms the stop 65, and is configured to come into abutment against a radial surface of the distribution ring 60 forming its distal end 60D , or near the distal end 60D.
  • the figure 9 shows another variant in which the stop 65 is formed by an insert positioned in a housing 67 formed in an internal groove, here the internal groove 50B.
  • the insert is for example a circlip, a ring, ring segment or half-ring, a pin or any other suitable element.
  • the stop 65 is formed by a pin.
  • this insert forms a stop 65 making it possible to limit the displacement of the core 50 relative to the distribution crown 60 in a direction going from the distal end 60D towards the proximal end 60P of the crown distribution 60.
  • a functional clearance is provided radially between the free end of the insert forming the stop and the axial wall of the associated groove.
  • the stop 65 is formed on one of the core 50 and the distribution ring 60, and is adapted to come into contact with one surface of the other among the core 50 and the timing ring 60.
  • the stop 65 is only used during the assembly of a hydraulic device. More generally, the stop 65 can be qualified as internal to the distributor 40, in that it does not require elements external to the distributor 40 to perform its function. Once the hydraulic device has been assembled, the stop 65 is no longer in contact with the core 50 in order to avoid generating additional friction between the core 50 and the timing ring 60.
  • the distributor 40 as proposed may also include a secondary stop such as an elastic ring or a cover in order to limit the relative displacement of the core 50 relative to the distribution crown 60 in the other direction, namely a displacement of the core 50 in the direction going from the proximal end 60P of the distribution crown 60 towards the distal end 60D of the distribution crown 60.
  • the secondary stop is typically removable.
  • the figure 10 is a variant of the figure 4 , in which an elastic ring 7 is inserted in a groove 67 arranged near the distal end 60D of the distribution ring 60.
  • Such elastic rings are commonly designated by the name "circlip”.
  • the elastic ring 7 here defines a stop limiting the relative displacement of the core 50 relative to the distribution ring 60 in the direction from the proximal end 60P of the distribution ring 60 towards the distal end 60D of the ring distribution 60; the distal end 50D of the core 50b then abuts against the elastic ring 7.
  • the figure 11 is another variant of the figure 4 , in which the elastic ring 7 is here positioned in a groove 57 arranged in the core 50, near its proximal end 50P.
  • the elastic ring 7 defines a stop limiting the relative displacement of the core 50 relative to the distribution ring 60 in the direction going from the proximal end 60P of the distribution ring 60 towards the distal end 60D of the timing ring 60; the elastic ring 7 then abuts against the proximal disengagement 63 of the distribution ring 60.
  • the figure 12 presents another embodiment of the secondary stop 7, which here has the shape of a cap.
  • the distribution ring 60 has an external groove 68 typically extending over its entire external periphery, in which are engaged fixing lugs 71 of the cover 7.
  • the cover 7 here at least partially covers the distal end 60D of the ring distribution 60, so as to define a stop limiting the relative displacement of the core 50 relative to the distribution ring 60 in the direction from the proximal end 60P of the distribution ring 60 towards the distal end 60D of the ring distribution 60, the distal end 50D of the core 50 then coming into contact with the cap 7.
  • the cap 7 typically has one or more openings in order to allow the passage of bolts, in particular for the assembly of the core 50 and the crown of distribution 60 on the other components of a hydraulic device while keeping the cap 7 in place, the latter then being removed following this assembly.
  • the figure 13 is an example of an embodiment of such a cap 7.
  • an operator will firstly position the bearings 18A and 18B as well as the housing segment 10C around the shaft 14, then the housing segment 10B. If the operator performs the assembly directly on a vehicle, the above elements are already assembled and constitute a wheel spindle on a hub. The operator will then place the cylinder block 12A and the cam 12B. It will then bring the distributor 40 in order to position it in abutment against the shaft 14 and against the cylinder block 14A as indicated previously (having optionally removed the secondary stop 7), the stop 65 then ensuring a function of maintaining in position of the segments 52 by keeping them sandwiched between the core 50 and the distribution ring 60. The operator then positions cover 10A which will hold the distributor 40 in position.
  • the distributor 40 as proposed thus makes it possible to facilitate the assembly operations of a hydraulic device comprising such a distributor, and thus avoids the risks of loss of time or damage to the distributor 40 resulting from a loss of segment 52 linked excessive movement of the core 50 relative to the distribution ring 60 while the distributor 40 has not yet been assembled with other components of the hydraulic device. These advantages also apply more generally for any transport operation, or involving manipulation of the dispenser 40 before mounting.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Automatic Assembly (AREA)
  • Sealing Devices (AREA)
  • Gasket Seals (AREA)

Claims (8)

  1. Verteiler (40) für ein hydraulisches Gerät, umfassend einen Kern (50) und einen Verteilerkranz (60), der um den Kern (50) entlang einer Achse (A) montiert ist, die ein proximales Ende (40P) und ein distales Ende (40D) definiert, wobei der Verteilerkranz (60) und der Kern (50) entlang der Achse (A) gleitend in Bezug aufeinander montiert sind,
    wobei der Kern (50) mehrere innere Rillen (50A, 50B) aufweist, die in einen äußeren Umfang des Kerns (50) münden,
    wobei der Verteilerkranz (60) mehrere äußere Rillen (60A, 60B) aufweist, die in einen inneren Umfang des Verteilerkranzes (60) münden,
    wobei die inneren (50A, 50B) und äußeren Rillen (60A, 60B) dazu ausgestaltet sind, in Fluidverbindung versetzt zu werden und Kanäle zum Umwälzen von Fluid zu bilden,
    wobei der Kern (50) mehrere Dichtsegmente (52) umfasst, die dazu ausgestaltet sind, jeden der Kanäle zum Umwälzen von Fluid zu isolieren,
    wobei der Kern (50) einen sich verringernden äußeren Querschnitt von einem distalen Ende (50D) zu einem proximalen Ende (50P) aufweist,
    wobei einer von dem Kern (50) und dem Verteilerkranz (60) einen Anschlag (65) umfasst, der auf solche Weise ausgestaltet ist, dass er mit einer Wand des anderen von dem Kern (50) und dem Verteilerkranz (60) in Kontakt gelangt, um die Verschiebung des Kerns (50) in Bezug auf den Verteilerkranz (60) gemäß einer Richtung, die durch die Achse (A) definiert wird, von dem distalen Ende (60D) zu dem proximalen Ende (60P) zu begrenzen,
    wobei jedes der Dichtsegmente (52) des Kerns (50) in einer Aufnahme (51) positioniert ist, die in den Kern (50) eingebracht ist, und gegen eine innere Fläche des Verteilerkranzes (60) anliegt,
    wobei der Verteiler (40) dadurch gekennzeichnet ist, dass der Anschlag (65) auf solche Weise ausgestaltet ist, dass er die Verschiebung des Kerns (50) in Bezug auf den Verteilerkranz (60) in einer Richtung, die durch die Achse (A) definiert wird, derart begrenzt, dass der Abstand zwischen dem proximalen Dichtsegment (52) und dem proximalen Abstand (63) des Verteilerkranzes (60) ungleich null bleibt,
    wobei das proximale Dichtsegment (52) das Dichtsegment (52) ist, das entlang der Achse (A) dem proximalen Ende (50P) des Kerns (50) am nächsten liegt, und der proximale Abstand (63) des Verteilerkranzes (60) definiert ist als die erste Variation des Querschnitts der inneren Oberfläche des Verteilerkranzes (60) in Anlage gegen das proximale Dichtsegment (52), in der Richtung von einem proximalen Ende (60P) des Verteilerkranzes (60).
  2. Verteiler nach Anspruch 1, wobei der Anschlag (65) fest mit dem Verteilerkranz (60) verbunden ist und auf solche Weise ausgestaltet ist, dass er mit einer Wand des Kerns (50) in Kontakt gelangt.
  3. Verteiler nach Anspruch 1, wobei der Anschlag (65) fest mit dem Kern (50) verbunden ist und auf solche Weise ausgestaltet ist, dass er mit einer Wand des Verteilerkranzes (60) in Kontakt gelangt.
  4. Verteiler nach einem der Ansprüche 1 bis 3, ferner umfassend einen sekundären Anschlag (7), der auf den Kern (50) oder auf den Verteilerkranz (60) aufgebaut ist, auf solche Weise, dass die Verschiebung des Kerns (50) in Bezug auf den Verteilerkranz (60) in einer Richtung, die durch die Achse (A) definiert wird, in einer Richtung durch den Anschlag (65) und in der anderen Richtung durch den sekundären Anschlag (7) begrenzt wird.
  5. Verteiler nach Anspruch 4, wobei der sekundäre Anschlag (7) ein elastischer Ring ist, der in einer Rille (57, 67) montiert ist, die in den Kern (50) oder in den Verteilerkranz (60) eingebracht ist.
  6. Verteiler nach Anspruch 4, wobei der sekundäre Anschlag (7) ein Element ist, das eine Abdeckung bildet, und um das distale Ende (60D) des Verteilerkranzes (60) montiert ist, wobei das Element, das eine Abdeckung bildet, eine Oberfläche aufweist, die einen Anschlag bei der Verschiebung des Kerns (50) in Bezug auf den Verteilerkranz (60) gemäß der Achse (A) in einer Richtung bildet, die von dem proximalen Ende (60P) zu dem distalen Ende (60D) des Verteilerkranzes (60) geht.
  7. Hydraulisches Gerät mit Radialkolben und Nocken mit mehreren Fortsätzen, umfassend einen Verteiler (40) nach einem der vorhergehenden Ansprüche, wobei ein Spiel (J) ungleich null gemäß der Achse (A) zwischen dem Anschlag (65) des Verteilers (40) und einer Oberfläche des Kerns (50) vorliegt, die zu dem Anschlag (65) hin weisend angeordnet ist.
  8. Verfahren zum Anbauen eines hydraulischen Geräts an einen Radachsschenkel, wobei
    eine erste Anordnung von Komponenten des hydraulischen Geräts um eine Achse (14) des Radachsschenkels positioniert wird,
    ein Verteiler (40) nach einem der Ansprüche 1 bis 6 bereitgestellt wird,
    der Verteiler (40) in Anlage gegen die Komponenten der ersten Anordnung von Komponenten so positioniert wird, dass ein Spiel (J) ungleich null entlang einer Achse (A) des Radachsschenkels zwischen dem Anschlag (65) des Verteilers und einer Oberfläche des Kerns (50) definiert wird, die zu dem Anschlag (65) hin weisend angeordnet ist,
    der Kern (50) mit einer Komponente der ersten Anordnung von Komponenten fest verbunden wird,
    eine zweite Anordnung von Komponenten des hydraulischen Geräts so positioniert wird, dass ein inneres Gehäusevolumen definiert wird, in welchem der Verteiler (40) positioniert wird.
EP18173896.4A 2017-05-24 2018-05-23 Hydraulisches gerät, das einen verbesserten verteiler umfasst Active EP3406901B1 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
FR1754608A FR3066789B1 (fr) 2017-05-24 2017-05-24 Appareil hydraulique comprenant un distributeur ameliore

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EP3406901B1 true EP3406901B1 (de) 2020-01-01

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Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2655090B1 (fr) * 1989-11-30 1993-03-19 Poclain Hydraulics Sa Mecanisme a fluide sous pression, tel qu'un moteur ou une pompe, attele a un dispositif de freinage.
FI110446B (fi) * 1997-11-11 2003-01-31 Valmet Hydraulics Oy Radiaalimäntähydraulimoottori
EP0921309B1 (de) * 1997-12-02 2003-03-19 Poclain Hydraulics Industrie Hydraulikmotor mit Schaltventil
FR3030381B1 (fr) * 2014-12-19 2018-10-19 Eugene Albert Laurent Moteur hydraulique pour roue de vehicule
FR3037354B1 (fr) * 2015-06-12 2019-05-10 Poclain Hydraulics Industrie Systeme hydraulique a chambre drainee

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

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EP3406901A1 (de) 2018-11-28
FR3066789A1 (fr) 2018-11-30

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