EP1941158B1 - Radialkolben-hydraulikmotor mit zylinderblockkühlung - Google Patents

Radialkolben-hydraulikmotor mit zylinderblockkühlung Download PDF

Info

Publication number
EP1941158B1
EP1941158B1 EP06831301.4A EP06831301A EP1941158B1 EP 1941158 B1 EP1941158 B1 EP 1941158B1 EP 06831301 A EP06831301 A EP 06831301A EP 1941158 B1 EP1941158 B1 EP 1941158B1
Authority
EP
European Patent Office
Prior art keywords
cylinder block
hole
rotation
sweep
fluid
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP06831301.4A
Other languages
English (en)
French (fr)
Other versions
EP1941158A1 (de
Inventor
Ante Bozic
Marièle Legai
Gilles Lemaire
Louis Bigo
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
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Poclain Hydraulics Industrie filed Critical Poclain Hydraulics Industrie
Publication of EP1941158A1 publication Critical patent/EP1941158A1/de
Application granted granted Critical
Publication of EP1941158B1 publication Critical patent/EP1941158B1/de
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Classifications

    • 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
    • F03C1/0415—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
    • F04B1/0404—Details or component parts
    • F04B1/0421—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 present invention relates to a radial piston hydraulic motor comprising a housing, a cylinder block arranged in the housing so that the housing and the cylinder block are able to rotate relative to each other about an axis. and having a plurality of cylinders which extend radially relative to the axis of rotation and in which pistons are slidably mounted, a reaction cam for the pistons, and a fluid distributor, which is integral with the cam with respect to the rotation about the axis of rotation and which comprises distribution ducts adapted to connect a supply line or an exhaust duct to the cylinders.
  • the invention is more particularly concerned with the cooling of the cylinder block of an engine of this type. Indeed, during the operation of the engine, overheating occurs in various areas of the engine and, if they are not controlled, these overheating adversely affect the transmission of engine power and may even cause damage to certain parts .
  • Certain areas of the engine are particularly affected by these heating phenomena. These are in particular the regions of the cylinder block and the pistons in which the friction between the pistons and the walls of the cylinders are the highest.
  • the heating up in these areas can lead to an increase in the diameter of the pistons, and consequently cause local deformations of the latter which cause the section of a piston to no longer be precisely matched to that of its cylinder, which further increases friction and therefore heating.
  • excessive heating can cause seizure of a piston in its cylinder and therefore irreversible damage to the cylinder block and the piston concerned, and usually the engine.
  • the friction relates more particularly cylindrical surfaces in contact between the pistons and the cylinders. More particularly, in the case of a radial piston engine, the friction is greatest in the vicinity of a radial plane (perpendicular to the axis of rotation), in which the diameters of the pistons can be measured.
  • Patent is also known US 3,151,529 a cylinder block having axial holes.
  • the invention aims to provide a hydraulic motor for which the cooling of the cylinder block is improved.
  • the cylinder block has scanning holes, which are formed between two consecutive cylinders, and which open at least two openings in two pressure zones different from the periphery of the cylinder block, each hole at least partly extending at least in the vicinity of a radial plane of the cylinder block in which the diameter of a cylinder adjacent to the hole in question and in the radial space of said cylinder is measured, so that fluid contained in the casing can circulate in the scanning hole in the vicinity of said cylinder to promote cooling of the wall of the latter in a zone passing through said radial plane.
  • the scanning holes of the invention are formed between the consecutive cylinders and are irrigated in sweeping fluid because the pressure difference between the two openings of a hole generates a flow of fluid in this hole. Indeed, the fluid tends to enter the scan hole through the opening in the vicinity of which the pressure of the fluid is the highest, and out through the other opening.
  • This pressure difference in the vicinity of the two openings exists in operation of the engine, during the relative rotation of the cylinder block and the cam. It may be inherent in the operation of the engine and be simply due to the arrangement of the two openings and / or the addition of specific means such as deflectors in the vicinity of the openings.
  • Each scanning hole extends between two consecutive cylinders, in the vicinity of the radial plane in which the heating is important and in the radial space of an adjacent cylinder, that is to say on at least a part of the height. of this cylinder. Consequently, these sweep holes allow the areas of the cylinder block more particularly concerned with the heating to be cooled and this cooling has an effect on the walls of the rolls and, therefore, on the pistons which slide against these walls.
  • the scanning holes have, over at least a portion of their length, a section that delimits a closed contour, so that they form enclosures in which the scanning fluid can flow.
  • the scanning holes behave like real ducts, in which the flushing fluid circulates through them from one side to the other.
  • At least one sweeping hole, open on the axial periphery of the cylinder block opposite the axis of rotation and situated in the vicinity of a cylinder is asymmetrical with respect to the radial plane in which the diameter of the cylinder is measured.
  • the fluid located in the vicinity of the axial periphery of the cylinder block opposite the axis of rotation tends to be driven tangentially.
  • the fluid flow tends to be distributed substantially symmetrically with respect to the radial plane in which the diameter of the cylinder is measured, generating two currents around the point of contact between the piston located in this cylinder and the cam.
  • At least one sweeping hole formed between two consecutive rolls comprises two openings respectively located, on the axial periphery of the cylinder block opposite the axis of rotation, in the vicinity of each of said rolls.
  • one of the openings is in front of one of the two cylinders while the other opening is behind the other cylinder. Due to the rotation, the fluid pressures contained in the casing in these two zones are different, which favors the circulation of the fluid in the scanning hole.
  • At least one scanning hole formed between two consecutive cylinders has two openings respectively located at each of the two axial ends of the cylinder block, and means are provided to promote the circulation of fluid in the scanning hole during the rotation. relative to the cylinder block and the crankcase.
  • the hole has at least one section inclined relative to the axis of rotation and / or a deflector is located in the vicinity of at least one of the openings of the sweeping hole, this deflector can be attached to the cylinder block or integrated therewith. This inclination and / or this reflector make it possible to ensure that the pressure of the fluid in the vicinity of the two openings is different.
  • At least one scanning hole comprises at least one opening located on the axial periphery of the cylinder block opposite the axis of rotation and an opening located on an axial end of the cylinder block.
  • the sweeping hole may have a bent shape and two openings respectively located on the axial end of the cylinder block and on the outer axial periphery of the latter.
  • a sweeping hole may also comprise a substantially rectilinear section which passes right through the cylinder block between its two axial ends, and an additional opening located on the outer axial periphery of the cylinder block. The openings are then located in very different areas of the cylinder block, so that the pressure in the vicinity of these openings is different. In particular, because of the relative rotation of the cylinder block and the cam, the pressure in the vicinity of the axial periphery of the cylinder block varies.
  • the fluid pressures around the axial periphery of the biocylinder vary locally depending on the position of the pistons, the distance between the cylinder block and the cam (recesses and peaks of the cam lobes) and the direction of rotation.
  • the pressure of the fluid does not vary or virtually no.
  • the cylinder block has at least one series of two sweep holes comprising a first sweeping hole having at least a first opening located on the axial end of the cylinder block located on the distributor side and a second opening located on the axial periphery of the cylinder block opposite to the axis of rotation and a second sweeping hole having at least a first opening on the axial periphery of the cylinder block opposite to the axis of rotation and a second opening on the end axial cylinder block opposite the distributor.
  • the sweeping fluid flows in the first sweep hole to emerge on the axial periphery of the cylinder block opposite to the axis of rotation and, from from this zone of the motor, circulates in the second sweeping hole to emerge on the other axial end of the cylinder block.
  • This configuration is particularly suitable in the case where the cylinder block comprises two rows of cylinders arranged one after the other in the axial direction, the cylinders of one row being arranged in staggered rows with respect to those of the other row. .
  • the circulation of the fluid in the sweeping holes is favored by the addition of an additional fluid introduced into the housing, originating for example from an exchange or swaging valve.
  • the cylinder block has blind sweeping holes, which are formed between consecutive cylinders, and which are open on the axial periphery of the cylinder block opposite to the axis of rotation, each sweeping hole extending at least in part at least in the vicinity of a radial plane of the cylinder block in which is measured the diameter of a cylinder adjacent to the hole in question and in the radial space of said cylinder, so that fluid contained in the casing can circulate in the scanning hole in the vicinity of said cylinder to promote the cooling of the wall of the latter in a zone passing through said radial plane, at least one blind sweep hole situated in the vicinity of a cylinder being asymmetrical by relative to the radial plane in which the diameter of the cylinder is measured.
  • This dissymmetry allows during the relative rotation of the cylinder block and the cam to create pressure variations generating a swirling effect, and thus to promote the circulation of fluid in the hole, although it is one-eyed.
  • the hydraulic motor shown on the figure 1 includes a three part housing, 1A, 1B and 1C.
  • a cylinder block 10 comprising a plurality of cylinders 12 in which pistons 14 are slidably mounted is disposed in this housing. It is a piston engine radial, the cylinders being oriented radially relative to the axis A of relative rotation between the cylinder block and the housing.
  • the housing is fixed while the cylinder block is rotating and drives in its rotation an output shaft 16 which is secured to it by splines 17. This rotation is supported relative to the housing by bearings 18.
  • a fluid distributor 20 which is fixed in rotation relative to the casing by being secured to it by a system with pins and notches 22.
  • the dispenser comprises distribution ducts 24 and 26 which are respectively connected to mains C1 and C2 for supplying and exhausting fluid.
  • these distribution ducts are alternately placed in communication with roll ducts 28 to push the pistons against the cam 30 or allow them to retract into their cylinders.
  • This cam 30 is formed on the inner periphery of the part 1B of the housing part and, as seen on the figure 2 it has a wavy shape.
  • the distribution is of radial type since the distribution ducts 24, 26 open on a radial face 32 of the distributor 20 which is perpendicular to the axis of rotation A, and which bears against a radial face 34 of the cylinder block 10.
  • the invention applies to radial piston engines in which the cam is rotating while the cylinder block is stationary, and also to radial piston engines in which the distribution is of the axial type and operates by axial faces facing the cylinder block and the distributor partially engaged in the latter.
  • the motor has scanning holes 40, which are formed between two consecutive cylinders 12.
  • these scanning holes 40 are open on the outer axial periphery 10A of the cylinder block, (opposite to the axis of rotation A).
  • a first variant corresponding to the radial section 41A shown in solid line, it concerns blind holes which pass through the radial plane PR mentioned above and extend, from the face 10A, to a depth sufficient to achieve neighborhood Z1 and Z2 areas mentioned above.
  • the blind hole is asymmetrical with respect to the radial plane PR in which the diameter of an adjacent cylinder is measured in order to promote the circulation of fluid in the blind hole, by a vortex effect at its inlet.
  • the section of the blind hole is advantageously oblong.
  • the radial portion 41A of the hole 40 is connected to an axial portion 41B (shown in broken lines) at its end located near the zones Z1 and Z2.
  • the holes 40 are also open on the axial end 10B or 10C of the cylinder block. They then advantageously have a L-shaped shape, with the radial section 41A and the axial section 41B. They could have a T-shape by being open on both axial ends of the cylinder block. It is possible to provide that the radial sections 41A of the holes 40 are centered on the radial plane PR.
  • these sections are advantageously asymmetrical with respect to this radial plane PR, as shown in FIG. figure 3 .
  • This allows to favor, by a swirl effect at the openings 40A of the holes 40, the circulation of fluid in the latter.
  • the openings 40A of the radial sections 41A are oblong, while the openings 40B of the radial sections 41B are circular. They could also be oblong.
  • the openings 40B are shown in phantom to show that they may or may not exist, depending on whether the holes 40 are blind or, conversely, open on the faces 10A and 10B of the cylinder block.
  • the fluid pressures around the axial periphery of the cylinder block vary during the relative rotation of the cylinder block and the cam.
  • the engine of the figure 2 is of the type with rotating cylinder block and with fixed cam
  • the sweeping hole 40 located in front of the piston at the upper part of the figure 2 whose axis AP is indicated it is found that the volume v1 of fluid downstream of this hole 40 decreases during the rotation of the cylinder block in the direction R1 so that the pressure increases locally in front of the piston, then that at the same time the volume v2 upstream of this hole 40 increases so that the pressure drops in this upstream zone.
  • the pressure at the axial ends of the cylinder block remain unchanged or substantially unchanged.
  • FIG 4 shows a scanning hole 50 formed between two consecutive cylinders 12A and 12B, and comprising two openings, respectively 50A and 50B, respectively located in the vicinity of the cylinders 12A and 12B. More specifically, if it is considered that the cam 30 is fixed while the cylinder block rotates relative to it in the direction of rotation R1, the opening 50A of the duct 50 is behind the cylinder 12A in an area whose volume v2 is being increased, while the opening 50B is in front of the cylinder 12B in this direction of rotation, in an area whose volume v1 is being reduced.
  • the opening 50B is in an area in which fluid is pushed by the piston 14 located in the cylinder 12B and is therefore in slight overpressure, while the opening 50A which is at the rear of the cylinder 12A is in an area where the fluid is in slight relative depression. This promotes the flow of fluid in the scan hole 50, the fluid entering through the opening 50B and out through the opening 50A.
  • the scan hole 50 is formed of two rectilinear sections 51 and 52 which move towards each other, as they approach the axis of rotation A, until they intersect with each other. connect these two sections.
  • the hole 50 can be made by two rectilinear machining inclined differently.
  • This sweeping hole thus having generally a V shape can be closed at the tip of the V.
  • the sections 51 and 52 can at this point communicate with a section of duct 54 directed substantially axially, as shown in broken lines on the figure 4 .
  • this section of duct 54 can be open on at least one of the axial ends 10B, 10C of the cylinder block.
  • the sweeping holes 60 formed between two consecutive cylinders 12 have two openings, 60A and 60B, respectively located on each of the two axial ends 10B and 10C of the cylinder block.
  • At least one deflector is located in the vicinity of one of the openings of this hole.
  • two deflectors 61A and 61B are respectively located in the vicinity of the openings 60A and 60B.
  • the orientation of these deflectors is such that when the cylinder block rotates in the direction R1 relative to the cam which is fixed, the deflector 61A promotes fluid entry through the opening 60A, while the reflector 61B promotes the fluid outlet through the opening 60B.
  • the deflector 61A increases the fluid pressure in the vicinity of the opening 60A, while the deflector 61B decreases it in the vicinity of the opening 60B.
  • the deflectors may be formed by plates, respectively, 62A and 62B, respectively fixed at the axial ends 10B and 10C of the cylinder block. It may be continuous plates having, in the vicinity of each opening, a locally rectified portion after cutting, or instead of a plate for each deflector.
  • the scanning holes 60 are directed substantially parallel to the axis of rotation A.
  • the scanning hole 60 ' also crosses the cylinder block from one side to the other by having two openings, respectively 60'A and 60'B, respectively located at the two axial ends 10B and 10C of the latter.
  • this hole is inclined relative to the axis A at an inclination angle ⁇ which is preferably of the order of 3 ° to 45 °, depending on the available space.
  • the shape shown for the sweep hole 60 'of the figure 6 can be adopted for all sweep holes or for at least some of them.
  • the scanning holes or at least some of them may consist of several sections of different inclinations, in which case the section whose inclination is the highest relative to the axis A is preferably located at inlet of the hole, that is to say in the vicinity of one end, 10B and / or 10C, of the cylinder block.
  • the scanning holes or some of them may even have a continuously variable inclination, the parts near the ends 10B and 10C of the cylinder block being the most inclined relative to the axis A, while the central portion may have a low inclination, or zero or substantially zero, with respect to this axis.
  • the inclination of the sweeping holes favors the entry of fluid into these holes.
  • the opening 60'A located on the end 10B of the cylinder block is located forward, in the direction of rotation, of the PB projection of the opening 60'B of the same sweeping hole located on the other axial end 10C, this projection being carried out parallel to the axis of rotation A.
  • This inclination promotes the entry of fluid through the opening 60 ' To which is located in front and is in slight overpressure, and the exit by the other opening.
  • the edges of the openings 60'A and 60'B can form integrated deflectors 61'A, 61'B made by local inflections of the inclination of the hole 60 'in the vicinity of these openings. These inflections are such that they further accentuate the fact that, in the direction of rotation R1, the opening 60'A is in front of the opening 60'B and that conversely, in the direction of rotation R2, the opening 60'B is in front of the opening 60'A.
  • the steep inclination of the hole 60 "in the vicinity of the ends 10B and 10C of the cylinder block also forms such integrated deflectors.
  • At least one scanning hole comprises at least one opening which is situated on the external axial periphery 10A of the cylinder block, and an opening located on an axial end 10B / 10C of the cylinder block.
  • a first possibility for this variant has been described with reference to Figures 1 to 3 .. It is also possible, in the same spirit, to modify the embodiment of the Figures 5 and 6 to add to one or more holes at least one section extending substantially radially, and connect the holes 60 or 60 'to the axial periphery of the cylinder block.
  • the figure 7 shows an exemplary embodiment for holes opening on different sides of the cylinder block.
  • the hole 70 comprises a substantially axial section 71 (which can be inclined as the holes 60 'of the figure 6 ), and two substantially radial sections, respectively 72 and 73, which connect the section 71 to the outer axial periphery 10A of the cylinder block.
  • These two sections 72 and 73 are located on either side of the radial plane PR, perpendicular to the axis of rotation A and in which is measured the diameter of the cylinders between which the hole 70 is formed.
  • This configuration makes it possible to favor the circulation indicated by the arrows of the figure 7 , forming two opposite circulation loops.
  • the fluid enters through the opening 71A of the section 71 located on the axial end 10B of the cylinder block and leaves through the opening 72A of the section 72 which is situated on the same side of the plane PR as this end 10B, while for the other loop, the fluid enters through the opening 71B of the section 71 located on the axial end side 10C of the cylinder block and leaves through the opening 73A of the section 73 located on the same side of the plane PR as this end 10C.
  • these loops constitute the preferred currents of circulation, but it is not excluded that they partially mix.
  • the fluid pressure varies at the apertures 72A and 73A during the relative rotation of the cylinder block and the cam, as previously discussed.
  • This configuration can make it possible to give the sections 72 and 73 relatively large sections because, not being located on the plane PR, they are formed in areas of the cylinder block in which two consecutive cylinders are not too close.
  • the section 71 can be substantially centered on the median plane between the two consecutive cylinders 12 between which the scanning hole 70 is formed, the sections 72 and 73 also being centered on this plane of symmetry PS.
  • the section 71 can be inclined and the sections 72 and 73 can be slightly offset relative to the plane PS to further promote the flow of fluid in a manner similar to that represented by the figure 4 , making for example the section 72 at the rear of the cylinder 12 which is located forward in the direction of rotation and the section 73 at the front of the cylinder which is located at the rear in the same direction of rotation.
  • the cylinder block rotates in the direction R2 relative to the cam, and the volume v2 in which the orifice 72 opens increases, thus causing a favorable depression to the fluid outlet through the orifice 72A .
  • volume v1 tends to decrease.
  • the figure 9 shows a variant in which the scan hole 80 also has a first opening 80A which opens on one axial end of the cylinder block, in this case the end 10B, and another opening 80B which opens on the outer axial periphery 10A of the cylinder block.
  • This hole 80 is formed of two sections, knowing of course that it could be modified to replace the substantially radial section which ends with the opening 80B by two sections of the type of the sections 72 and 73 of the figure 8 .
  • the sweeping hole 80 is open on the axial end 10B of the cylinder block against which the distributor 20 bears, in a space E which is separated from the part 1B of the housing containing the cam 30 by an obstacle 82 favoring the fluid flow within this space through the scan hole 80.
  • the obstacle 82 may be in the form of a ring, which is attached to the housing portion 1C so that its free end opposed to this part 1C is located in the vicinity of the radial face of the cylinder block forming the end 10B, or in contact with it.
  • the fluid contained in the space E naturally tends to escape to the outside, under the effect of the centrifugal force.
  • the obstacle 82 prevents or limits this natural tendency, and therefore forces the fluid to pass through the scanning hole 80, this scanning hole being situated between the axis of rotation A and the obstacle 82 which is advantageously located at a distance radial axis A adjacent to that which is the axial periphery 10A of the cylinder block or near the opening 80A.
  • the presence of the obstacle 82 causes an overpressure in the vicinity of the opening 80A of the hole 80, while the pressure is lower in the vicinity of the other opening 80B.
  • a fluid sweeping system of the motor housing As indicated above, it is advantageous to provide a fluid sweeping system of the motor housing.
  • a scanning duct 38 is formed in the part 1C of the casing, so as to open into the space E.
  • the sweeping fluid thus injected which has been advantageously cooled by an exchange system, thus passes through the hole of sweeping 80 before irrigating the rest of the housing, to achieve the desired cooling of the cylinder block.
  • the embodiment of the figure 9 can know several variants, in particular the sweeping hole can also be open on the end 10C of the cylinder block opposite the end 10B. Insofar as the fluid is naturally driven by the effect of the centrifugal force, this does not prevent a significant amount of fluid escaping through the opening 80B.
  • this series comprises a first scanning hole 90 having a first opening 90A located on the axial end 10B of the cylinder block 10, and two openings, respectively 90B and 90C, located on the outer axial periphery 10A of the cylinder block .
  • this first hole 90 comprises a first section 91 which extends between the first opening 90A and, substantially, the median radial plane PM of the cylinder block, and two substantially radial sections. respectively 92 and 93, which respectively connect the openings 90B and 90C to the first section 91.
  • This series comprises a second scanning hole 94 which has two first openings, 94A and 94B, respectively, which are located on the outer axial periphery 10A of the cylinder block, and a second opening 94C, which is located at the end 10C of the block -cylinders opposite to the distributor.
  • the second hole 94 has a conformation similar to that of the first hole 90, but it is arranged inverted with respect to the median plane PM. It therefore comprises a substantially axial section 95 which opens at the opening 90C, and two substantially radial sections 96 and 97, which open respectively to the openings 94A and 94B.
  • the circulation of the sweeping fluid in the two holes 90 and 94 is effected in the manner indicated by the arrows, the fluid initially located on the side of the axial end 10B of the cylinder block entering through the opening 90A to exit through openings 90B and 90C, then entering again through openings 94A and 94B to exit through opening 94C.
  • the fluid located in the casing may emerge through a leakage return duct 39 in order, in particular, to undergo a heat exchange.
  • the embodiment of the figure 10 particularly relates to the case where the cylinder block 10 comprises two rows of cylinders arranged in two slices of the cylinder block. These two slices each extend over a portion of the length of the cylinder block, on either side of the median plane PM, or slightly intersecting on this plane.
  • the first scan holes 90 are located between two consecutive cylinders 12 of the first slice C1 cylinders whose diameters are measured in the radial plane PR1
  • the second scan pipe holes 94 are located between two consecutive cylinders of the second slice of cylinders C2 whose diameters are measured in the radial plane PR2.
  • the sections 92 and 93 of the first hole 90 are located on either side of the radial plane PR1, and the sections 96 and 97 are located on either side of the radial plane PR2.
  • this is not limiting, one could instead substantially center the second sections of the conduits on these respective radial planes PR1 and PR2. It is desirable that the sections 91 and 95 of the ducts 90 and 94 extend respectively from the axial ends 10B and 10C of the cylinder block, at least to the radial planes PR1 and PR2, respectively.
  • the first scan holes 90 and the second scan holes 94 are angularly offset relative to each other.
  • the cylinders of a slice are advantageously arranged substantially staggered with respect to those of the other slice, in particular for reasons of space. Under these conditions, it is not easy to form the scanning holes so that they pass directly through the cylinder block from one side, between its two axial ends 10B and 10C.
  • the configuration that has just been described, however, makes it possible to perform the scanning for both sets of cylinders, using the fluid leaving the scanning holes used for one of the series, to irrigate the sweeping holes used for the two sets of cylinders. other series.
  • this embodiment is compatible with that described with reference to the figure 9 , that is to say that the space E situated between the axial end 10B of the cylinder block and the part 1C of the housing, on the side of the distributor 20, is confined by an obstacle 82 which makes it possible to ensure that the fluid in the space E, in particular the flushing fluid supplied by a flushing duct 38, naturally has a tendency to escape through the flushing holes 90.
  • an obstacle 98 similar to the obstacle 82 is disposed on the opposite side of the cylinder block.
  • This obstacle 96 may also be formed by a ring fixed to the part 1A of the housing and whose free end comes into contact with or in the immediate vicinity of the end 10C of the cylinder block. This makes it possible to prevent the fluid that has emerged through the orifices 90B and 90C from the first scanning holes 90 being brought directly towards the leakage return duct 39 without first passing through the second scanning holes 94.
  • the figure 12 still shows a variant, wherein at least one scanning hole 100 located between two consecutive cylinders is open towards an axial end of the cylinder block in a space, which is supplied with sweeping fluid and which is delimited by at least one obstacle favoring the flow of the sweeping fluid outside this space through the sweeping hole.
  • the scan hole 100 has an opening 100A which is located in an area of the cylinder block adjacent to the axis of rotation A and the distributor 20.
  • This opening is in this case located in the immediate vicinity of the axial end 10B of the cylinder block. Indeed, in some cases, it is advantageous to take advantage of the central space 27 of the distributor to supply the casing of the fluidizer for sweeping by a valve V sweeping or exchange. In this case, the position of the opening 100A allows it to be easily supplied with sweep fluid and the valve V provides an overpressure at the inlet 100A relative to the outlet 100B.
  • the obstacle which promotes the flow of the sweeping fluid outside this space 27 is formed by the contact between the distribution face 32 of the distributor and the communication face 34 of the cylinder block.
  • the zone of the cylinder block in which the opening 100A is located is defined radically by the contact zone between the distributor and the cylinder block.
  • the scanning hole 100 also opens on the outer axial periphery 1QA of the cylinder block.
  • figure 12 (the section 101 being inclined relative to the radial plane PR from the opening 100A, while the section 102 is oriented radially), and / or to provide several openings 100B located on the outer axial periphery 10A of the cylinder block, for example by being located on either side of the radial plane PR.
  • the figure 13 illustrates a possibility of modifying the variant of the figure 12 , in which the scanning hole 100 ', which further has a configuration similar to that of the hole 100 of the figure 12 , is further open on the axial ends 10B and 10C of the cylinder block by two openings respectively 100'C and 100'D.
  • the centrifugal force to which the fluid flowing in the hole is subjected As a result, the fluid that has entered through opening 100A has a natural tendency to escape through opening 100B, while fluid also tends to enter through openings 100'C and 100'D.
  • This variant also has the advantage, at low rotational speed and therefore in the presence of a small centrifugal force, to promote the flow of the fluid operating as an ejector. Indeed, the kinetic energy of the exchange fluid or sweep passing in the section 101 creates an additional flow of fluid by driving the fluid from the housing to the 100'D and 100'C inputs.
  • the holes and sections of holes of the different variants may have a circular, substantially circular, oblong, substantially oblong or any other shape that can be obtained by casting or forging, combined or not with machining, this shape being able to have a variable section to reduce the thickness of the wall between the sweeping fluid and the friction zone.
  • holes can be made between each group of two consecutive cylinders of a row of cylinders, but they can also be made only on only part of this row.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Hydraulic Motors (AREA)

Claims (13)

  1. Radialkolben-Hydraulikmotor, umfassend ein Gehäuse (1A, 1 B, 1 C), einen Zylinderblock (10), der in dem Gehäuse angeordnet ist, so dass das Gehäuse und der Zylinderblock geeignet sind, sich um eine Rotationsachse (A) relativ zueinander zu drehen, und der eine Vielzahl von Zylindern (12) aufweist, die sich zu der Rotationsachse radial erstrecken und in denen Kolben (14) verschieblich angebracht sind, einen Reaktionsnocken (30) für die Kolben und einen Fluidverteiler (20), der gegenüber der Drehung um die Rotationsachse (A) fest mit dem Nocken verbunden ist und der Verteilungsleitungen (24, 26) umfasst, welche geeignet sind, eine Zuführleitung oder eine Abführleitung (C1, C2) mit den Zylindern (12) zu verbinden,
    dadurch gekennzeichnet, dass der Zylinderblock (10) Spüllöcher (40; 50; 60; 60'; 60"; 70; 80; 90, 94; 100; 100') aufweist, die zwischen zwei aufeinanderfolgenden Zylindern (12) ausgebildet sind und die über wenigstens zwei Öffnungen (40A, 40B; 50A, 50B; 60A, 60B; 60'A, 60'B; 71A, 71 B, 72A, 73A; 80A, 80B; 90A, 90B, 90C, 94A, 94B, 94C; 100A, 100B; 100'A, 100'B, 100'C, 100'D) in zwei Bereiche mit unterschiedlichem Druck des Umfangs des Zylinderblocks (10) münden, wobei jedes Spülloch sich wenigstens teilweise wenigstens in der Nähe einer Radialebene (PR) des Zylinderblocks, in welcher der Durchmesser eines zu dem betrachteten Loch benachbarten Zylinders (12) gemessen wird, und in der radialen Abmessung des Zylinders erstreckt, derart, dass in dem Gehäuse enthaltenes Fluid in dem Spülloch (40; 50; 60; 60'; 60"; 70; 80; 90, 94; 100; 100') in der Nähe des Zylinders (12) zirkulieren kann, um die Kühlung der Wand des letzteren in einem durch die Radialebene (PR) verlaufenden Bereich zu begünstigen.
  2. Motor nach Anspruch 1, dadurch gekennzeichnet, dass wenigstens ein Spülloch (40), das an dem von der Rotationsachse (A) abgewandten axialen Umfang (10A) des Zylinderblocks (10) offen und in der Nähe eines Zylinders (12) gelegen ist, in Bezug auf die Radialebene (PR), in welcher der Durchmesser des Zylinders gemessen wird, unsymmetrisch ist.
  3. Motor nach Anspruch 1 oder 2, dadurch gekennzeichnet, dass wenigstens ein Spülloch (50), das zwischen zwei aufeinanderfolgenden Zylindern (12A, 12B) ausgebildet ist, zwei Öffnungen (50A, 50B) umfasst, die jeweils auf dem von der Rotationsachse (A) abgewandten axialen Umfang (10A) des Zylinderblocks (10), in der Nähe eines jeden der Zylinder (12A, 12B) gelegen sind.
  4. Motor nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, dass wenigstens ein Spülloch (60; 60'; 60"), das zwischen zwei aufeinanderfolgenden Zylindern ausgebildet ist, zwei Öffnungen aufweist, die jeweils an jedem der beiden axialen Enden (10B, 10C) des Zylinderblocks gelegen sind, und dass Mittel (61A, 61B; 61'A, 61'B) angeordnet sind, um die Fluidzirkulation in dem Spülloch im Laufe der Relativdrehung des Zylinderblocks (10) und des Gehäuses (1 A, 1 B, 1 C) zu begünstigen.
  5. Motor nach Anspruch 4, dadurch gekennzeichnet, dass das Spülloch (60'; 60") in Bezug auf die Rotationsachse (A) derart geneigt ist, dass im Laufe der Drehung des Zylinderblocks in einer Drehrichtung (R1) die Öffnung (60'A), welche sich an einem der axialen Enden (10B) des Zylinderblocks (10) befindet, in der Drehrichtung vor der Projektion (PB) auf dieses axiale Ende der an dem anderen axialen Ende (10C) befindlichen Öffnung (60'B) gelegen ist, wobei diese Projektion parallel zu der Rotationsachse (A) ausgeführt ist.
  6. Motor nach Anspruch 4 oder 5, dadurch gekennzeichnet, dass die Mittel zum Begünstigen der Fluidzirkulation in dem Spülloch (60; 60', 60") im Laufe der Relativdrehung des Zylinderblocks (10) und des Gehäuses (1 A, 1 B, 1 C) wenigstens einen Deflektor (61A, 61B; 61'A, 61'B), der in der Nähe von einer der Öffnungen (60A, 60B; 60'A, 60'B) dieses Lochs gelegen ist, umfassen.
  7. Motor nach einem der Ansprüche 1 bis 6, dadurch gekennzeichnet, dass wenigstens ein Spülloch (70; 80; 90, 94; 100; 100') wenigstens eine Öffnung (72A, 73A; 80B; 90B, 90C; 94A, 94B; 100B), welche auf dem von der Rotationsachse (A) abgewandten axialen Umfang (10A) des Zylinderblocks (10) gelegen ist, und eine Öffnung (71A, 71B; 80A; 90A, 94C; 100A), welche an einem axialen Ende (10B, 10C) des Zylinderblocks (10) gelegen ist, umfasst.
  8. Motor nach Anspruch 7, dadurch gekennzeichnet, dass der Zylinderblock (10) wenigstens eine Reihe von zwei Spüllöchern aufweist, die ein erstes Spülloch (90) mit wenigstens einer ersten Öffnung (90A), die an dem auf der Seite des Verteilers (20) befindlichen axialen Ende (10B) des Zylinderblocks (10) gelegen ist, und einer zweiten Öffnung (90B), die auf dem von der Rotationsachse (A) abgewandten axialen Umfang (10A) des Zylinderblocks gelegen ist, sowie ein zweites Spülloch (94) mit wenigstens einer ersten Öffnung (94A, 94B), die auf dem von der Rotationsachse (A) abgewandten axialen Umfang (10A) des Zylinderblocks gelegen ist, und einer zweiten Öffnung (94C), die an dem von dem Verteiler abgewandten axialen Ende (10C) des Zylinderblocks (10) gelegen ist, umfasst.
  9. Motor nach einem der Ansprüche 1 bis 8, dadurch gekennzeichnet, dass wenigstens ein Spülloch (80; 90) an einem axialen Ende (10B) des Zylinderblocks (10), an dem der Verteiler (20) in Anlage ist, in einen Raum (E) geöffnet ist, der von dem den Nocken (30) enthaltenden Teil des Gehäuses (1 B) durch ein Hindernis (82), das das Strömen des Fluids aus diesem Raum (E) über das Spülloch (80; 90) begünstigt, getrennt ist.
  10. Motor nach einem der Ansprüche 1 bis 9, dadurch gekennzeichnet, dass wenigstens ein Spülloch (80; 90; 100; 100') an einem axialen Ende (10B) des Zylinderblocks (10) in einen Raum (E; 27) geöffnet ist, der mit Spülfluid beaufschlagt wird und der durch wenigstens ein Hindernis (82), welches das Strömen des Spülfluids aus diesem Raum über das Spülloch begünstigt, begrenzt ist.
  11. Motor nach einem der Ansprüche 1 bis 10, dadurch gekennzeichnet, dass wenigstens ein Spülloch (100; 100') wenigstens eine in einem zu der Rotationsachse (A) und zu dem Verteiler (20) benachbarten Bereich des Zylinderblocks (10) gelegene Öffnung (100A) aufweist, die mit Spülfluid beaufschlagt wird und die durch einen Kontaktbereich zwischen dem Verteiler (20) und dem Zylinderblock (10) radial begrenzt ist.
  12. Radialkolben-Hydraulikmotor, umfassend ein Gehäuse (1 A, 1 B, 1 C), einen Zylinderblock (10), der in dem Gehäuse angeordnet ist, so dass das Gehäuse und der Zylinderblock geeignet sind, sich um eine Rotationsachse (A) relativ zueinander zu drehen, und der eine Vielzahl von Zylindern (12) aufweist, die sich zu der Rotationsachse radial erstrecken und in denen Kolben (14) verschieblich angebracht sind, einen Reaktionsnocken (30) für die Kolben und einen Fluidverteiler (20), der gegenüber der Drehung um die Rotationsachse (A) fest mit dem Nocken verbunden ist und der Verteilungsleitungen (24, 26) umfasst, welche geeignet sind, eine Zuführleitung oder eine Abführleitung (C1, C2) mit den Zylindern (12) zu verbinden,
    dadurch gekennzeichnet, dass der Zylinderblock (10) Spülsacklöcher (40) aufweist, die zwischen aufeinanderfolgenden Zylindern (12) ausgebildet sind und die an dem von der Rotationsachse (A) abgewandten axialen Umfang (10A) des Zylinderblocks offen sind, wobei jedes Spülloch sich wenigstens teilweise wenigstens in der Nähe einer Radialebene (PR) des Zylinderblocks, in welcher der Durchmesser eines zu dem betrachteten Loch benachbarten Zylinders (12) gemessen wird, und in der radialen Abmessung des Zylinders erstreckt, derart, dass in dem Gehäuse enthaltenes Fluid in dem Spülloch (40) in der Nähe des Zylinders (12) zirkulieren kann, um die Kühlung der Wand des letzteren in einem durch die Radialebene (PR) verlaufenden Bereich zu begünstigen, wobei wenigstens ein Spülsackloch (40), das in der Nähe eines Zylinders (20) gelegen ist, in Bezug auf die Radialebene (PR), in welcher der Durchmesser des Zylinders gemessen wird, unsymmetrisch ist.
  13. Motor nach Anspruch 12, dadurch gekennzeichnet, dass die Spülsacklöcher (40) einen länglichen Querschnitt aufweisen.
EP06831301.4A 2005-10-27 2006-10-26 Radialkolben-hydraulikmotor mit zylinderblockkühlung Active EP1941158B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR0511021A FR2892775B1 (fr) 2005-10-27 2005-10-27 Moteur hydraulique a pistons radiaux avec refroidissement du bloc-cylindres
PCT/FR2006/051109 WO2007048979A1 (fr) 2005-10-27 2006-10-26 Moteur hydraulique a pistons radiaux avec refroidissement du bloc-cylindres

Publications (2)

Publication Number Publication Date
EP1941158A1 EP1941158A1 (de) 2008-07-09
EP1941158B1 true EP1941158B1 (de) 2017-05-24

Family

ID=36699007

Family Applications (1)

Application Number Title Priority Date Filing Date
EP06831301.4A Active EP1941158B1 (de) 2005-10-27 2006-10-26 Radialkolben-hydraulikmotor mit zylinderblockkühlung

Country Status (5)

Country Link
EP (1) EP1941158B1 (de)
JP (1) JP4889742B2 (de)
CN (1) CN101297111B (de)
FR (1) FR2892775B1 (de)
WO (1) WO2007048979A1 (de)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2940672B1 (fr) * 2008-12-31 2011-01-21 Poclain Hydraulics Ind Moteur hydraulique a pistons radiaux et commande par cylindre
FR2940671B1 (fr) * 2008-12-31 2011-04-22 Poclain Hydraulics Ind Circuit de transmission hydraulique
FR2996267B1 (fr) * 2012-09-28 2014-10-03 Poclain Hydraulics Ind Appareil hydraulique presentant une structure amelioree pour sa mise en cylindree
FR3019594B1 (fr) 2014-04-02 2016-04-08 Poclain Hydraulics Ind Section additionnelle de poussee
CN104863781A (zh) * 2015-05-29 2015-08-26 杭州电子科技大学 具有仿生非光滑表面织构的低速大扭矩水液压马达
FR3121960B1 (fr) * 2021-05-19 2023-04-14 Poclain Hydraulics Ind Circuit de balayage amélioré pour machine hydraulique.

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
NL66843C (de) * 1938-12-21 1950-11-16
US2855858A (en) * 1957-04-12 1958-10-14 Bendix Aviat Corp Positive displacement pump
US3151529A (en) * 1962-05-22 1964-10-06 Harry A Leath Motor
DE3721698A1 (de) * 1987-07-01 1989-01-19 Hauhinco Maschf Radialkolbenpumpe fuer die foerderung von wasser
CN2142892Y (zh) * 1992-05-26 1993-09-29 邱作儒 内冷式放射型转子压缩机
WO2001077495A1 (de) * 2000-04-11 2001-10-18 Mannesmann Rexroth Ag Radialkolbenmaschine
FR2834012B1 (fr) * 2001-12-24 2004-03-19 Poclain Hydraulics Ind Moteur hydraulique a pistons radiaux

Non-Patent Citations (1)

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

Also Published As

Publication number Publication date
FR2892775B1 (fr) 2010-11-05
CN101297111A (zh) 2008-10-29
EP1941158A1 (de) 2008-07-09
JP2009513869A (ja) 2009-04-02
FR2892775A1 (fr) 2007-05-04
JP4889742B2 (ja) 2012-03-07
CN101297111B (zh) 2011-06-08
WO2007048979A1 (fr) 2007-05-03

Similar Documents

Publication Publication Date Title
EP1941158B1 (de) Radialkolben-hydraulikmotor mit zylinderblockkühlung
FR2563582A1 (fr) Plateau de distribution pour unite hydraulique
FR3046811A1 (fr) Aube directrice de sortie pour turbomachine d'aeronef, presentant une fonction amelioree de refroidissement de lubrifiant
FR3049644A1 (fr) Aube directrice de sortie pour turbomachine d'aeronef, presentant une fonction amelioree de refroidissement de lubrifiant a l'aide d'une matrice de conduction thermique logee dans un passage interieur de l'aube
WO2004020800A1 (fr) Gicleur a projections multiples pour refroidissement de moteur, et moteurs equipes de tels gicleurs
FR2887287A1 (fr) Circuits de refroidissement pour aube mobile de turbomachine
WO2018100278A1 (fr) Aube directrice de sortie pour turbomachine d'aeronef, comprenant une zone coudee de passage de lubrifiant presentant une conception amelioree
FR2715448A1 (fr) Anneau de friction et embrayage comportant un tel anneau.
FR2995341A1 (fr) Roue de turbine d'une machine fluidique et son procede de fabrication
FR3077850A1 (fr) Aube directrice de sortie pour turbomachine, realisee a partir de plusieurs pieces assemblees entre elles par des moyens de fixation deportes de la veine
FR2901577A3 (fr) Piston de moteur a combustion interne pourvu de moyens specifiques de refroidissement et moteur a combustion interne comprenant un tel piston
FR2511432A1 (fr) Piston de moteur a surfaces d'appui distinctes
FR3066532B1 (fr) Aube directrice de sortie pour turbomachine d'aeronef, comprenant un passage de refroidissement de lubrifiant equipe de plots perturbateurs de flux a fabrication simplifiee
WO2012176037A1 (fr) Moteur a combustion interne avec transmission a calage variable
FR2834013A1 (fr) Procede et appareil de lubrification d'un compresseur du type a piston.
FR2758376A1 (fr) Carter de rotor d'un convertisseur de couple et procede pour former ce carter
FR3086006A1 (fr) Piston pour moteur a combustion interne
CA2492844C (fr) Actionneur hydraulique de soupapes pour moteur a pistons
FR3013774B1 (fr) Pompe d'injection de carburant a lubrification integree a l'axe de rotation du galet
FR2950926A1 (fr) Moteur a pistons rotatifs
EP3244034B1 (de) Brennkraftmotor mit einer kühlflüssigkeitspumpe
FR3054622A1 (fr) Ensemble piston bielle rotulee avec passage d’huile par une contre-rotule
FR3068406B1 (fr) Paliers et module d'embrayage pour vehicule automobile
FR3055387B1 (fr) Ensemble piston bielle rotulee avec augmentation de vitesse d’un flux d’huile interne
FR2850439A1 (fr) Dispositif pour la transformation d'un mouvement rotatif en mouvement rectiligne, et inversement, comprenant une came interagissant avec au moins un piston

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20080331

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): DE FR GB

RBV Designated contracting states (corrected)

Designated state(s): DE FR GB

DAX Request for extension of the european patent (deleted)
GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

INTG Intention to grant announced

Effective date: 20161202

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAJ Information related to disapproval of communication of intention to grant by the applicant or resumption of examination proceedings by the epo deleted

Free format text: ORIGINAL CODE: EPIDOSDIGR1

GRAL Information related to payment of fee for publishing/printing deleted

Free format text: ORIGINAL CODE: EPIDOSDIGR3

GRAR Information related to intention to grant a patent recorded

Free format text: ORIGINAL CODE: EPIDOSNIGR71

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

INTC Intention to grant announced (deleted)
AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE FR GB

INTG Intention to grant announced

Effective date: 20170419

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 602006052648

Country of ref document: DE

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 12

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 602006052648

Country of ref document: DE

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 602006052648

Country of ref document: DE

26N No opposition filed

Effective date: 20180227

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20180501

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 13

P01 Opt-out of the competence of the unified patent court (upc) registered

Effective date: 20230513

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20231019

Year of fee payment: 18

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20231023

Year of fee payment: 18