EP3408539B1 - Kolben für eine drehkolbenpumpe - Google Patents

Kolben für eine drehkolbenpumpe Download PDF

Info

Publication number
EP3408539B1
EP3408539B1 EP17702831.3A EP17702831A EP3408539B1 EP 3408539 B1 EP3408539 B1 EP 3408539B1 EP 17702831 A EP17702831 A EP 17702831A EP 3408539 B1 EP3408539 B1 EP 3408539B1
Authority
EP
European Patent Office
Prior art keywords
plates
rotary piston
polymer material
plate
spacer element
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
EP17702831.3A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP3408539C0 (de
EP3408539A1 (de
Inventor
Thomas Hinners
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.)
Hugo Vogelsang Maschinenbau GmbH
Original Assignee
Hugo Vogelsang Maschinenbau GmbH
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 Hugo Vogelsang Maschinenbau GmbH filed Critical Hugo Vogelsang Maschinenbau GmbH
Publication of EP3408539A1 publication Critical patent/EP3408539A1/de
Application granted granted Critical
Publication of EP3408539B1 publication Critical patent/EP3408539B1/de
Publication of EP3408539C0 publication Critical patent/EP3408539C0/de
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/12—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C2/126—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with radially from the rotor body extending elements, not necessarily co-operating with corresponding recesses in the other rotor, e.g. lobes, Roots type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0003—Sealing arrangements in rotary-piston machines or pumps
    • F04C15/0007—Radial sealings for working fluid
    • F04C15/0015—Radial sealings for working fluid of resilient material
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0003—Sealing arrangements in rotary-piston machines or pumps
    • F04C15/0023—Axial sealings for working fluid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C18/082—Details specially related to intermeshing engagement type pumps
    • F04C18/084—Toothed wheels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C18/12—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C18/126—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with radially from the rotor body extending elements, not necessarily co-operating with corresponding recesses in the other rotor, e.g. lobes, Roots type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C18/12—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C18/14—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
    • F04C18/16—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/082—Details specially related to intermeshing engagement type machines or pumps
    • F04C2/084—Toothed wheels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/12—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C2/14—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
    • F04C2/16—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2230/00—Manufacture
    • F04C2230/20—Manufacture essentially without removing material
    • F04C2230/23—Manufacture essentially without removing material by permanently joining parts together
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/20—Rotors

Definitions

  • the invention relates to a rotary piston for a rotary piston pump for conveying particle-laden liquids.
  • the invention relates to a rotary piston pump, comprising a housing with a housing interior, an inlet opening through which liquid can flow into the housing interior, an outlet opening through which liquid can flow out of the housing interior, a first rotary piston which is mounted so as to rotate about a first axis of rotation within the housing interior, and a second rotary piston which is mounted so as to rotate about a second axis of rotation within the housing interior, wherein the first rotary piston and the second rotary piston engage with one another in a region between the first and second axes and displace liquid.
  • a further aspect of the invention is a method for producing a rotary piston for such a rotary piston pump and a rotary piston for such a rotary piston pump.
  • Rotary lobe pumps are fluid conveying devices that are mainly used for liquids with low or high viscosity.
  • Rotary lobe pumps work on the principle that two counter-rotating rotary lobes rotate around two spaced apart, parallel axes and mesh in such a way that a rotary lobe of one rotary lobe engages in a rotary lobe recess between two rotary lobes of the other piston.
  • the liquid is displaced in the middle region between the two axes by the meshing and in the two outer peripheral areas outside the two Axes of rotation in delivery chambers, which result from the rotary piston recesses in sealing the two surrounding rotary piston blades or their rotary piston blade tips against the housing wall, conveyed from the inlet to the outlet opening.
  • Rotary lobe pumps can be equipped with rotary lobes that have two, three or more rotary lobe vanes.
  • Rotary lobe pumps are used in a specific application to pump particle-laden liquids.
  • One problem with pumping particle-laden liquids is the high level of wear that occurs on various pump components.
  • Rotary lobe pumps are generally better suited to pumping particle-laden liquids than other pump designs, but are also subject to high levels of wear.
  • This wear is caused by particles that either become trapped between the rotary pistons or between the outer ends of the rotary piston vanes and the housing wall, thereby causing indentations or grinding marks in the surfaces of the housing wall or the rotary pistons.
  • Rotary pistons are manufactured from a metal according to the state of the art and are manufactured to such an exact fit that efficient conveying with low leakage rates is possible. It is known to equip rotary pistons with a surface rubber layer in order to counteract wear effects when conveying particle-laden liquids. The effect underlying this measure is that the rubber layer makes the rotary pistons suitable to a limited extent for allowing particles that are trapped between the rotary pistons or between the rotary piston blades and the housing wall to penetrate their rubberized surface through brief elastic or plastic deformation without suffering permanent or serious damage. This can prevent the formation of deep impressions, wear marks and other wear effects and improve the wear behavior of rotary piston pumps when conveying particle-laden liquids.
  • the invention is based on the object of proposing an improved rotary piston pump for pumping particle-laden liquids within this optimization problem.
  • a rotary piston for a rotary piston pump which has a framework arrangement which comprises a plurality of plates spaced apart from one another and the framework arrangement is at least partially filled and at least partially encased with a polymer material, wherein spacer elements hold the plates at a predetermined distance from one another, wherein one spacer element is formed integrally on each plate, wherein each plate has at least one spacer element stop surface which lies at a predetermined height above the plate plane and is in contact with an adjacent plate at its end pointing away from the plate plane, wherein the spacer elements are produced by angular deformation of a portion of the plate.
  • the problems in the prior art are overcome by implementing a completely different internal design of the rotary piston.
  • the rotary piston is constructed from several plates spaced apart from one another as a framework arrangement. This framework arrangement is at least partially covered and filled with a polymer material.
  • the rotary piston designed according to the invention is designed in particular in such a way that - apart from a central opening for receiving a drive shaft - it does not have any air-filled Cavities, i.e. it is filled with either plate material or polymer material in its interior.
  • the plates are preferably arranged in such a way that their surface is aligned perpendicular to the axis of rotation of the rotary piston.
  • the plates therefore define in particular the cross-sectional geometry of the rotary piston by having a corresponding inner contour and a corresponding outer contour.
  • the inner contour defines the inner central opening of the
  • Rotary piston with which the rotary piston is received on a drive shaft.
  • This inner recess is preferably designed to transmit torque, for example by having a polygonal cross-sectional geometry or is designed in another form for a positive torque transmission.
  • the plates directly define the geometry of the inner, central opening of the rotary piston, i.e. are not coated with the polymer material in the area of this inner opening of the rotary piston in order to achieve a defined angular position of the rotary piston relative to the drive shaft, which is free from elastic influences of the polymer material.
  • the rotary piston according to the invention can have a hub with an internal opening through which a drive shaft can be inserted or which can be connected to a drive shaft in a torque-tight manner in another way.
  • the plates have an inner central opening with which they can be mounted on the outer geometry of this hub and preferably fastened thereon in a torque-tight manner. It is further preferred that the plates on the outer surface of the rotary piston are completely coated with polymer material in order to avoid direct contact of the housing with the plates or between the plates when in contact with the housing wall or the other rotary piston.
  • the plates are preferably made of a material that has a higher rigidity, i.e. a lower elasticity, and a higher strength than the polymer material.
  • the plates can be made of a non-metal or at least partially comprise one in order to reduce the weight of the piston.
  • the carrier material As a framework arrangement consisting of several plates.
  • the boundary layer between the polymer material and the metallic core in rotary pistons according to the prior art can no longer occur with the structure of the rotary pistons according to the invention, since the boundary layer between the framework arrangement and the polymer material takes up a much larger area and can also be formed essentially with surfaces that are perpendicular to the axial direction. This surface orientation is much less sensitive to such infiltration and delamination than radially outward-facing peripheral boundary surfaces.
  • Cross-linking is understood here in the sense of Invention is to be understood as a process in which molecules combine with one another by forming new chemical compounds or change by replacing a first type of chemical compound with another type of chemical compound.
  • cross-linking is to be understood as polymerization or vulcanization.
  • the rotary pistons designed according to the invention are lighter than rotary pistons of known design, whereby the total weight of a rotary piston pump according to the invention is reduced compared to conventional rotary piston pumps. It is also advantageous that the rotary pistons according to the invention are manufactured using less metallic material at the expense of a higher proportion of polymer material, whereby the manufacturing costs in terms of material costs are reduced.
  • the plurality of spaced-apart plates are aligned parallel to one another and/or that the distance between two spaced-apart, adjacent plates is the same.
  • two, three, four or even more plates can be used to produce a rotary piston and the space between these plates can be filled with polymer material accordingly.
  • the framework arrangement of the plates is preferably completely filled with polymer material and preferably the outer surface of the rotary piston is completely covered with polymer material, whereas the inner opening of the rotary piston, which serves to transmit torque-locking power from a drive shaft to the rotary piston, is preferably not covered with polymer material.
  • a spacer element between every two plates, which extends over a predetermined height above a plate plane and at its end pointing away from the plate plane End are in contact with another plate, in particular an adjacent plate, wherein the spacer element is produced by angular deformation of a portion of the plate.
  • the production of a rotary piston according to the invention can in particular be carried out in such a way that several plates, which form the framework arrangement of the rotary piston, are positioned in a mold in a defined position relative to one another and then the filling/enveloping with the polymer material takes place within this mold.
  • the definition of the distance between the individual plates takes place by separate spacer elements or by the geometry of the plates themselves, for example by a spacer element being formed on the plates or inserted between two plates.
  • These spacer elements form the function of a spacer between the plates.
  • a single spacer element between two plates can fulfill this function and position the plates in a defined position relative to one another and a defined distance from one another.
  • the position of the plates in relation to the axis of rotation of the rotary piston can be defined, for example by appropriate position support against the hub of the rotary piston.
  • the function of spacing and, if necessary, positioning the plates can also be provided by a multi-part spacer element, for example a spacer element that consists of two, three, four or more spacer element pieces that are inserted between two adjacent plates.
  • a multi-part spacer element for example a spacer element that consists of two, three, four or more spacer element pieces that are inserted between two adjacent plates.
  • at least three spacer element pieces are preferred, so that a defined angular position of the plates to one another, in particular a parallel alignment of the plates to one another, is achieved by the multi-part spacer element.
  • the number of spacer element pieces that form a spacer element between two plates can in particular correspond to the number of rotary vanes of the piston, so that for rotary pistons with 2, 3, 4, 5 or 6 vanes, spacer elements are used that are composed of 2, 3, 4, 5 or 6 spacer element pieces, respectively.
  • a spacer element can also preferably be formed integrally on a plate, i.e. made in one piece with the plate.
  • the spacer element is produced by bending a portion of the plate.
  • a web formed on one side of the plate can be bent in such a way that it is at an angle of approximately 90° to the plate surface and thus represents the spacer element.
  • a web section that is connected to the plate on both sides can be deformed out of the plate plane by deformation, so that it can, for example, in a V-shaped contour above the plate plane and represents the spacer element.
  • the plates are sheets made of metallic material and/or the polymer material is a rubber-elastic material.
  • the manufacture of the plates from a metallic material enables a particularly robust framework arrangement which can withstand the operating forces, in particular the forces required to transmit torque from the drive shaft to the rotary piston.
  • the provision of the plates from a metallic material in the form of sheets enables in particular a cost-effective manufacture of the plates by punching or laser cutting the plates from a semi-finished material in the form of sheets and the manufacture of the spacer elements by cold forming a corresponding section or several sections of these sheets.
  • the polymer material can in particular be a rubber-elastic material which tolerates the elastic embossing of particles without damaging the polymer material. This particularly includes rubber-based polymer materials which are produced by a vulcanization process, but other materials with similar rubber properties can also be used for the rotary piston according to the invention.
  • the polymer material is formed by a prefabricated polymer component which is inserted in a cross-linked state through openings in the plates which are aligned with one another, and a polymer material portion which is formed by flowable polymer material which at least partially envelops the plates and the prefabricated polymer component in a flowable state and then cross-links them to a solid state.
  • the polymer material is formed by two different portions. The first portion is a prefabricated, already cross-linked component which, after the plates have been assembled, is inserted through corresponding openings in these plates. This prefabricated polymer component is then enveloping by a second polymer material portion and thereby fixed in its position relative to the plates. The two portions form a coherent polymer structure.
  • the advantage of the rotary piston designed in this way is that, on the one hand, a large proportion of polymer material can be realized in the rotary piston, and, on the other hand, it avoids the rotary piston being produced by cross-linking a large proportion of polymer material within the framework arrangement, which therefore has a large and poorly predictable shrinkage.
  • an already cross-linked polymer component is used to fill a large proportion of the volume within the framework arrangement with polymer material and only a small The volume portion within the framework arrangement is then filled/encased with a flowable polymer material, which is then cross-linked and shrinks in the process.
  • the prefabricated polymer component and the polymer material portion consist of the same polymer material, thereby achieving a particularly good connection between the prefabricated polymer component and the polymer material portion enveloping it.
  • several prefabricated polymer components can also be used in a rotary piston.
  • the plates have several openings distributed over the circumference, so that a plate, for example, has a cross-sectional geometry modeled on a spoked wheel and the several cavities formed between the spokes are filled with correspondingly contoured polymer components.
  • the mechanical connection between the polymer material and the plates is formed by an adhesive connection, by a positive connection between openings in the plates that are filled with polymer material, or by a force-fitting connection by means of clamping elements that clamp the plates and the polymer material together.
  • an adhesive connection can be achieved directly between the polymer material and the plates; to reinforce or to create such an adhesive connection, the framework arrangement can also be coated with a primer or an adhesive that is different from the polymer material before the polymer material is added.
  • This adhesive connection can correspond in particular to the adhesive connection used in rubber-metal elements in the field of vibration damping between the rubber and the metal part of such rubber-metal elements.
  • a positive connection can be achieved between openings in the plates and polymer material passed through them. These openings in the plates can be deliberately provided for this purpose, for example in the manner of the previously explained plate structure in the form of a spoked wheel, but other structures such as perforated plate elements or the like may also be advantageous for such a form-fitting effect.
  • a force-fitting connection between the plates and the polymer material can also be achieved, i.e. an adhesion achieved by a frictional force between the plates and the polymer material.
  • the normal force required for this frictional force can then be achieved by bracing the plates and the Polymer material can be achieved, for example, by providing screws perpendicular to the plate plane between the outer plates of the rotary piston, which press these two outer plates together in the axial direction.
  • a single one of these connection mechanisms or several of these connection mechanisms can act simultaneously to create the connection between the plates and the polymer material.
  • the second rotary piston has a framework arrangement which comprises a plurality of plates spaced apart from one another and the framework arrangement is at least partially filled and at least partially encased with a polymer material.
  • the second rotary piston like the first rotary piston, is constructed with a framework arrangement made of a plurality of plates and a polymer material. It should be understood in principle that the first and second rotary pistons of the rotary piston pump can be of identical construction and the second rotary piston can also be designed in accordance with the previously explained embodiments.
  • first and/or the second rotary piston has an internal non-circular opening, which is formed by an opening in the plates that is not filled with the polymer material, and that the first or second rotary piston is rotatably mounted via a first or second shaft that is arranged in this opening.
  • a recess or opening in the rotary piston makes it possible to arrange the rotary pistons in a form-fitting manner on a shaft that is designed to be congruent with the opening and to set them in rotation by this shaft.
  • the plates can be fastened in a form-fitting manner to a hub, which in turn is fastened to the shaft, for example in a force-fitting or form-fitting manner.
  • the recess or opening is formed by corresponding recesses or openings in the plates of the framework arrangement, which consequently cause the torque to be transmitted from the drive shaft to the framework arrangement.
  • a polygonal recess can be provided in the plates or the rotary pistons; a hexagonal opening that interacts with a corresponding hexagonal shaft or hexagonal hub is particularly suitable.
  • other configurations for the positive locking are also possible, for example keyways in an otherwise circular recess, which are designed for positive locking with a corresponding cylinder section of the shaft or hub with a corresponding key.
  • both rotary pistons are connected to a drive shaft in a torque-locking manner and these drive shafts are synchronized via an external gear, so that both rotary pistons are driven independently of each other but synchronously.
  • only one of the Both rotary pistons must be coupled and driven in a torque-locking manner via a shaft, and the other rotary piston is set into synchronous rotation by the engagement with this rotary piston without itself being driven via a shaft.
  • This other rotary piston therefore only needs to be mounted so that it can rotate, so that a circular recess without torque transmission to the shaft can also be considered here.
  • the first and the second rotary piston have at least two rotary piston vanes that run in a helical line along the outer circumference of the rotary pistons and that the plates have a corresponding geometry with at least two rotary piston vanes, wherein all plates are geometrically identical and the helical course is brought about by means of a non-circular, helical outer contour of a drive shaft or hub that is in positive engagement with a central recess of the plates, or the plates are divided into at least two sets that are pushed onto a shaft or hub with a straight, non-circular outer contour, wherein the plates within a set have a matching geometry and the plates of two different sets have a different geometry such that the angular position between a non-circular contour of a central opening and the rotary piston vanes between the plates of two different sets is different from one another.
  • the rotary piston vanes can extend along an axially aligned line that runs parallel to the rotary piston's axis of rotation.
  • Rotary piston pumps with such linear rotary piston vanes typically exhibit pulsation during delivery operation, which is caused by the defined delivery in the delivery chambers that form between the rotary piston vanes and the housing wall.
  • the pulsation of the delivery can be reduced or completely avoided if the rotary piston vanes run along a helically wound line.
  • This design is particularly suitable for rotary pistons with more than two rotary piston vanes, i.e. three, four or more rotary pistons, since this design reliably seals the chambers between the rotary piston vanes and the housing wall.
  • the contour of the rotary piston is predetermined by the framework arrangement up to the rotary piston vanes.
  • the framework arrangement must depict or have the helical course of the rotary piston vanes.
  • the plates that form the framework of a rotary piston can be geometrically identical.
  • the rotary piston wing depicted in a plate compared to the image of the same rotary piston vane in an adjacent plate by a predefined angle, which is calculated from the pitch of the helix and the distance between the two plates the plates in this case must be arranged on the drive shaft at an angular offset from one another.
  • two or more different sets of plates can also be provided in order to produce the framework arrangement of a rotary piston according to the design according to the invention.
  • the drive shaft or hub is provided with a non-circular outer contour, which is, however, designed to be straight, i.e. parallel to the longitudinal axis of the drive shaft, and consequently does not have a helical course. Plates of different geometries are then pushed onto this drive shaft or hub, whereby these plates differ in that the angular position of the rotary piston vanes in relation to the non-circular contour of the central recess of the plate is different from one another.
  • the rotary piston is designed as a three-vane rotary piston, i.e. each plate has three rotary piston vanes that are offset from one another by an angle of 120°.
  • the first set of plates is provided with a keyway in a central circular recess that is at an angular position of zero to a rotary piston vane.
  • a second set of plates is manufactured, which has an angle of 40° between the keyway and the rotary piston vane.
  • a third set of plates is manufactured, which has an angle of 80° between the keyway and the rotary piston vane.
  • this rotary piston can be built up in such a way that one plate of the first set, one plate of the second set, one plate of the third set and then Again, a plate from the first set, followed by a plate from the second set and a plate from the third set are arranged in such a way that the keyways of the plates are aligned with each other.
  • the advantage of this embodiment is the simple and cost-effective manufacture of the drive shaft or hub, which can be designed as a conventional cylinder shaft or hollow hub with a keyway in the outer peripheral surface or with a hexagonal outer surface.
  • a further aspect of the invention is a method for producing a rotary piston for a rotary piston pump, comprising the steps of: forming a framework arrangement by providing a plurality of plates spaced apart from one another, at least partially enveloping the plates with a polymer material in a flowable state, and creating a connection between the framework arrangement and the polymer material by crosslinking the polymer material, wherein two plates each are spaced apart and positioned parallel to one another by at least one spacer element piece formed on the plates, which is provided by producing the plates from sheet metal and bending at least one section of the sheet metal accordingly on each plate.
  • a particularly suitable polymer material is a rubber-elastic material, such as a rubber-based rubber material, which is brought into its mechanically solid form and into an adhesive connection to the framework arrangement by vulcanization.
  • the process can be further developed by positioning the plates parallel to one another using spacer elements formed on the plates.
  • the plates are made of sheet metal and that a spacer element is formed between two plates, for example by bending one or three sections of the sheet metal.
  • the method can be further developed by prefabricating the polymer material by crosslinking a first portion of the polymer material before forming the framework arrangement, arranging the prefabricated polymer component in mutually aligned openings in the plates, and at least partially enveloping the plates and the polymer component with a second portion of the polymer material in the state of a flowable polymer material, and crosslinking or curing the second portion of the polymer material to a solid state.
  • a further aspect of the invention is a rotary piston pump for conveying particle-laden liquids, comprising a housing with a housing interior, an inlet opening through which liquid can flow into the housing interior, an outlet opening through which liquid can flow out of the housing interior, a first rotary piston which is mounted so as to rotate about a first axis of rotation within the housing interior, and a second rotary piston which is mounted so as to rotate about a second axis of rotation within the housing interior, wherein the first rotary piston and the second rotary piston engage with one another in a region between the first and second axes and displace liquid, wherein the first rotary piston is a piston according to the invention.
  • This rotary piston is on the one hand cost-effective, on the other hand it is a precise fit and particularly resistant to abrasion, wear and delamination of the polymer material from the framework arrangement.
  • the rotary piston can in particular be further developed as was previously described for a rotary piston that is used in a rotary piston pump according to the invention.
  • the rotary piston can also be further developed by producing it using a method of the type described previously.
  • a three-bladed rotary piston with twisted rotary piston blades 41, 42, 43 that follow a helix is shown.
  • the invention is applicable to rotary pistons with straight rotary piston blades or twisted rotary piston blades or rotary piston blades with a geometry that differs therefrom and can be used for rotary pistons with two, three, four, five or more rotary piston blades.
  • the rotary piston according to the invention has a rotary piston hub 10, which is typically made of a metallic material.
  • the rotary piston hub has a cylindrical inner geometry with a groove 11 for a torque-resistant connection to a drive shaft by means of a feather key.
  • other shaft-hub connections can also be used that are suitable for transmitting a torque from the shaft to the hub, for example polygonal shafts that interact with a corresponding inner geometry of a polygonal hub, conical connections that connect the shaft to the hub by means of a force-fitting connection, gearing between the shaft and the hub and the like.
  • the rotary piston hub is surrounded by three rotary piston blades 41-43, which are arranged with a 120° pitch around the circumference of the rotary piston hub and wind in the axial direction of the rotary piston hub by approximately 60° in the circumferential direction along a helical line.
  • the degree of twist should be selected depending on the number of vanes in order to achieve pulsation-free operation, leak-free pumping action and protection against backflow through the pump in any rotational position of the rotary pistons.
  • the vanes should be twisted by more than 90°, with three-vane pistons, the vanes should be twisted by more than 60°, with four-vane pistons, the vanes should be twisted by more than 45° and generally the vanes should be twisted by more than 180° divided by the number of vanes.
  • the rotary piston blades are coated with a polymer material on their flanks as well as on their tips and front sides. This polymer material is also partially formed in the interior of the rotary piston blades; the exact design is explained in detail below.
  • the polymer material used is preferably a rubber-elastic material, which can in particular be a rubber material hardened by vulcanization.
  • the framework construction comprises several framework plates 20a, b, c, d, ... which basically correspond to the cross-sectional contour in an axial cross-section of the rotary piston, but are smaller in their dimensions than the cross-sectional dimension.
  • Each framework plate therefore has three vanes 21, 22, 23 which are arranged at a pitch of 120° to one another.
  • each framework plate has a central recess 24, see Figure 6 and 7 . This central recess is designed in such a way that it creates a torque-resistant connection between the framework plate and the rotary piston hub.
  • the recess is essentially circular and has three grooves 25 distributed over the circumference, which interact in a form-fitting manner with three congruent webs 12, 13, 14 on the outer surface of the rotary piston hub, as can be seen from Figure 5 visible.
  • the torque-resistant connection between the framework plate and the rotary piston hub can be designed in different ways; as an alternative to the embodiment shown here, embodiments with a single groove and a correspondingly single web can also be designed; alternatively, other types of connection with a toothing or the like can be designed.
  • the circumferential length of the grooves in the framework plate is approximately 60°, so that an even distribution of the three recessed circumferential parts and the three protruding circumferential parts of the central recess 24 in the framework plate results.
  • the groove-shaped recess is arranged in the area of the rotary piston blades in order to enable favorable material utilization and a narrow design of the framework plate in the area between the rotary piston blades.
  • Each framework plate further has a circular recess 26, 27, 28 in each rotary piston wing.
  • the framework plates of the rotary piston according to the invention are therefore designed with maximum material savings, given the outer contour of the rotary piston and a torque-resistant connection in direct contact with the rotary piston hub.
  • the webs 12, 13, 14 run in the axial longitudinal direction along the circumferential surface of the rotary piston hub along a helical line which corresponds to the helical course of the rotary piston vanes.
  • the inner framework of the rotary piston according to the preferred embodiment can therefore be constructed from several framework plates, which are all designed in the same way.
  • other configurations of the inventive rotary piston is conceivable and advantageous in certain applications.
  • an embodiment in which the webs are designed in a straight line in the axial longitudinal direction on the rotary piston hub can also be advantageous.
  • this design results in a rotary piston with straight rotary piston blades.
  • a helical course of the rotary piston blades can be achieved by alternately using framework plates that are designed differently.
  • This different design must consist in the angular offset between the grooves 25 on the one hand and the rotary piston blade sections 21, 22, 23 on the other hand being different for the various designs of the framework plates.
  • the angle difference results from the desired pitch of the rotary piston blades along the helical course and the axial distance of the framework plates on the rotary piston hub.
  • the rotary piston according to the invention is made up of a total of ten framework plates. These framework plates are arranged on the rotary piston hub at an axially uniform distance over the entire axial length of the rotary piston. Two adjacent framework plates are positioned relative to one another by three spacer element pieces 30, which form a spacer element. Instead of assembling the spacer element from three spacer element pieces, it is advantageous in some applications to manufacture the spacer element in one piece in order to simplify assembly, for example by connecting the three spacer element pieces to one another via webs or the like.
  • a spacer element 30 is in the Fig.8 and 9 shown.
  • the spacer element piece 30 has a substantially ring-shaped body which has a central axial recess 31.
  • a circumferential shoulder 32 is formed on one end face of the spacer element piece 30. The outer diameter of this shoulder 32 is slightly smaller than the inner diameter of the circular recesses 26, 27, 28 in the framework plates and thus allows a positive, centered positioning of the spacer element piece 30 within these recesses.
  • the spacer element piece is formed with a flat end face.
  • a corresponding circumferential shoulder can also be formed on the opposite side, which achieves a defined positioning of two adjacent framework plates relative to one another.
  • the shoulders on the two end faces can be coaxial to one another; when using the spacer elements for a rotary piston with helical
  • the steps must be designed with a corresponding eccentric offset to one another along the course of the rotary piston blades.
  • Each spacer element piece 30 also has a rounded recess 33 in a peripheral section, the radius of which corresponds to the radius of the outer surface of the rotary piston hub.
  • the spacer element pieces can thus be positioned so that they rest directly on the rotary piston hub and are secured against rotation.
  • a rotary piston according to the invention is constructed by a framework which comprises several framework plates 20 and three spacer elements 30 between two adjacent framework plates.
  • This construction provides a resilient framework structure which defines the contour of the rotary piston blades and has a positive connection to the rotary piston hub.
  • the framework plates are preferably made from a metallic material.
  • the spacer elements can preferably be made from a polymer material.
  • the framework construction with the rotary piston hub constructed in this way is then filled and covered with the polymer material.
  • This filling and covering process can be carried out in particular in such a way that three already hardened, for example vulcanized, polymer strands are pushed through the openings 26, 27, 28 of the framework plates, whereby it is particularly advantageous if an elastically deformable polymer material with an outer diameter that is slightly smaller than the inner diameter of these openings is used for this purpose in order to be able to follow the helical course in which these openings are staggered relative to one another.
  • prefabricated vulcanizable polymer strands can also be inserted into the openings, in which case the vulcanization of the polymer strands takes place during the subsequent vulcanization of the coating or covering with the remaining polymer material.
  • the framework structure prepared in this way with the prefabricated polymer parts already used can be overmolded and covered with a liquid polymer material, whereby the cavities within the framework structure are completely filled. Due to the high volume proportion of already cured and cross-linked polymer material, a low shrinkage of the polymer material is achieved during its cross-linking.
  • a staggered, two-stage overmold with the liquid polymer material can also be carried out in order to achieve a filling up to or slightly below the outer edge of the framework sheets in a first overmold and to achieve the complete outer contour in a second overmold that follows. by covering the framework.
  • the material thickness depends on the application and the overall dimensions of the rotary piston, for example, a material thickness of at least 5 mm of polymer material can be provided between the outer edges of the framework plates and the outer contour of the rotary piston.
  • the rotary piston according to the invention Due to its design, the rotary piston according to the invention has a rigid construction that can withstand high torque. At the same time, the proportion of metallic material is significantly reduced, which significantly reduces the weight of the rotary piston and the consumption of valuable raw materials.
  • the production of the rotary piston is considerably simplified due to the possible modularity with the use of the same components. For example, by using different rotary piston hubs with different pitches of the webs or lengths on them, rotary pistons with different pitches of the rotary piston blades or different lengths can be manufactured in a modular system.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
  • Rotary Pumps (AREA)
EP17702831.3A 2016-01-28 2017-01-27 Kolben für eine drehkolbenpumpe Active EP3408539B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE202016100419.5U DE202016100419U1 (de) 2016-01-28 2016-01-28 Kolben für eine Drehkolbenpumpe
PCT/EP2017/051853 WO2017129794A1 (de) 2016-01-28 2017-01-27 Kolben für eine drehkolbenpumpe

Publications (3)

Publication Number Publication Date
EP3408539A1 EP3408539A1 (de) 2018-12-05
EP3408539B1 true EP3408539B1 (de) 2024-05-01
EP3408539C0 EP3408539C0 (de) 2024-05-01

Family

ID=57960430

Family Applications (1)

Application Number Title Priority Date Filing Date
EP17702831.3A Active EP3408539B1 (de) 2016-01-28 2017-01-27 Kolben für eine drehkolbenpumpe

Country Status (11)

Country Link
US (1) US10982671B2 (zh)
EP (1) EP3408539B1 (zh)
JP (1) JP2019503454A (zh)
KR (1) KR20180123019A (zh)
CN (1) CN108700063A (zh)
AU (1) AU2017213147B2 (zh)
CA (1) CA3013104A1 (zh)
DE (1) DE202016100419U1 (zh)
MX (1) MX2018009213A (zh)
MY (1) MY198166A (zh)
WO (1) WO2017129794A1 (zh)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102017007832A1 (de) * 2017-08-22 2019-02-28 Pumpenfabrik Wangen Gmbh Verfahren zur Herstellung eines Drehkolbens für eine Schraubenspindelpumpe
DE202022104701U1 (de) 2022-08-19 2023-11-22 Vogelsang Gmbh & Co. Kg Verdrängerkörper und Pumpengehäuse für eine Verdrängerpumpe
DE102022003188A1 (de) 2022-09-01 2024-03-07 Peter Groppenbächer Vorrichtung zur Förderung von Fördergut
CN116696772A (zh) * 2023-05-06 2023-09-05 北京通嘉宏瑞科技有限公司 转子片、转子及真空泵

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3918838A (en) * 1974-01-04 1975-11-11 Dunham Bush Inc Metal reinforced plastic helical screw compressor rotor

Family Cites Families (21)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1499462U (zh) *
US2362106A (en) * 1941-04-21 1944-11-07 Equi Flow Inc Laminated gear pump
US2451603A (en) * 1944-10-04 1948-10-19 Virgil D Barker Rotary pump
DE3007267A1 (de) 1980-02-27 1981-09-03 Leybold Heraeus Gmbh & Co Kg Wellendichtung fuer waelzkolbenpumpen
GB8806242D0 (en) 1988-03-16 1988-04-13 Ibex Eng Co Ltd Improved lobe pump
US4913629A (en) * 1988-08-26 1990-04-03 Gilfillan William C Wellpoint pumping system
DE69213179T2 (de) 1991-10-17 1997-04-10 Ebara Corp Schraubenspindelrotor und Verfahren zu dessen Herstellung
BE1010376A3 (nl) 1996-06-19 1998-07-07 Atlas Copco Airpower Nv Rotatieve kompressor.
DE19839501A1 (de) * 1998-08-29 2000-03-02 Leybold Vakuum Gmbh Trockenverdichtende Schraubenspindelpumpe
US6688867B2 (en) 2001-10-04 2004-02-10 Eaton Corporation Rotary blower with an abradable coating
GB0224862D0 (en) 2002-10-25 2002-12-04 Aesseal Plc An intelligent sealing system
GB0228641D0 (en) 2002-12-06 2003-01-15 Adams Ricardo Ltd Improvements in or relating to rotors for rotary machines
DE10338180B3 (de) * 2003-08-17 2005-04-28 Erich Roos Verfahren zur Herstellung einer Extruderschnecke, sowie eine danach hergestellte Extruderschnecke
DE202006007501U1 (de) * 2006-05-11 2007-09-13 Hugo Vogelsang Maschinenbau Gmbh Drehkolbenpumpe
US20080170958A1 (en) * 2007-01-11 2008-07-17 Gm Global Technology Operations, Inc. Rotor assembly and method of forming
JP4431184B2 (ja) 2008-06-13 2010-03-10 株式会社神戸製鋼所 スクリュ圧縮装置
GB2490517B (en) 2011-05-04 2017-12-13 Edwards Ltd Rotor for pump
DE202012010401U1 (de) 2012-10-31 2014-02-03 Hugo Vogelsang Maschinenbau Gmbh Drehkolbenpumpe mit Direktantrieb
CN205089597U (zh) * 2012-11-20 2016-03-16 伊顿公司 用于罗茨型装置的转子和罗茨型装置
EP2971776A2 (en) 2013-03-15 2016-01-20 Eaton Corporation Low inertia laminated rotor
CN106414938B (zh) 2014-05-30 2020-06-30 伊顿智能动力有限公司 复合旋转部件

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3918838A (en) * 1974-01-04 1975-11-11 Dunham Bush Inc Metal reinforced plastic helical screw compressor rotor

Also Published As

Publication number Publication date
US20190048872A1 (en) 2019-02-14
DE202016100419U1 (de) 2017-05-02
WO2017129794A1 (de) 2017-08-03
CA3013104A1 (en) 2017-08-03
EP3408539C0 (de) 2024-05-01
US10982671B2 (en) 2021-04-20
JP2019503454A (ja) 2019-02-07
AU2017213147A1 (en) 2018-08-16
AU2017213147B2 (en) 2021-08-05
BR112018015305A2 (pt) 2018-12-18
MX2018009213A (es) 2019-05-23
KR20180123019A (ko) 2018-11-14
EP3408539A1 (de) 2018-12-05
MY198166A (en) 2023-08-08
CN108700063A (zh) 2018-10-23

Similar Documents

Publication Publication Date Title
EP3408539B1 (de) Kolben für eine drehkolbenpumpe
EP3535496B1 (de) Elektrische gerotorpumpe
EP2122174B1 (de) Integrierte innenzahnradpumpeneinheit mit elektrischem motor
EP3333381B1 (de) Hydraulikvorrichtung mit dichtelement
EP3507496B1 (de) Trockenverdichtende vakuumpumpe
WO2019002206A1 (de) Schraubenspindelpumpe, kraftstoffförderaggregat und kraftstofffördereinheit
EP3054179A1 (de) Welle eines gasturbinentriebwerks in faserverbundbauweise
DE102016121237B4 (de) Hydraulische Gerotorpumpe und Herstellungsverfahren einer Gerotorpumpe
DE102012215587A1 (de) Lasteinleitungselement
WO2016134884A1 (de) Rotor für eine elektrische maschine mit vorteilhafter drehmomentübertragung sowie entsprechende elektrische maschine
WO2014108116A1 (de) Nockenwellenversteller
EP1801418A1 (de) Planeten-Zahnradpumpe
EP2565463B1 (de) Vakuumpumpe
WO2012010262A1 (de) Kolbeneinheit
DE102015005790A1 (de) Schnecke zum Einsatz in einem Extruder, Verfahren zum Umrüsten einer Schnecke und Extruder
EP3507495A1 (de) Schraubenvakuumpumpe
DE102008034422A1 (de) Rotor für einen elektronisch kommutierten Motor
DE102018130557A1 (de) Rotorwelle für einen Rotor eines Elektromotors
DE102019005367B4 (de) Verfahren zur Herstellung eines Statorbauteil für eine Exzenterschneckenpumpe, Statorbauteil und Exzenterschneckenpumpe
EP2063126A2 (de) Hydraulische Zahnradmschine und Verfahren zum Abdichten einer hydraulischen Zahnradmaschine
WO2008101904A1 (de) Gerotorpumpe
AT518670B1 (de) Kurvenscheibe für Zykloidengetriebe und deren Herstellung
WO2016139230A1 (de) Rotationskolbenpumpe
WO2023126119A1 (de) Stator für eine exzenterschneckenpumpe
DE102012206698A1 (de) Hydrostatische Verdrängermaschine mit einer Gehäusetrennfläche, welche die Drehachsen der Zahnräder enthält

Legal Events

Date Code Title Description
STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: UNKNOWN

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

Free format text: STATUS: THE INTERNATIONAL PUBLICATION HAS BEEN MADE

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

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

Free format text: STATUS: REQUEST FOR EXAMINATION WAS MADE

17P Request for examination filed

Effective date: 20180828

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

AX Request for extension of the european patent

Extension state: BA ME

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

Free format text: STATUS: REQUEST FOR EXAMINATION WAS MADE

DAV Request for validation of the european patent (deleted)
DAX Request for extension of the european patent (deleted)
REG Reference to a national code

Ref country code: HK

Ref legal event code: DE

Ref document number: 1259967

Country of ref document: HK

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

Free format text: STATUS: EXAMINATION IS IN PROGRESS

17Q First examination report despatched

Effective date: 20210209

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

Free format text: STATUS: EXAMINATION IS IN PROGRESS

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

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

Free format text: STATUS: GRANT OF PATENT IS INTENDED

INTG Intention to grant announced

Effective date: 20231204

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

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

Free format text: STATUS: THE PATENT HAS BEEN GRANTED

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

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: CH

Ref legal event code: EP

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 502017016079

Country of ref document: DE

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

Free format text: LANGUAGE OF EP DOCUMENT: GERMAN

U01 Request for unitary effect filed

Effective date: 20240523

U07 Unitary effect registered

Designated state(s): AT BE BG DE DK EE FI FR IT LT LU LV MT NL PT SE SI

Effective date: 20240604