[go: up one dir, main page]
More Web Proxy on the site http://driver.im/

EP3439789B1 - High-pressure rotor nozzle - Google Patents

High-pressure rotor nozzle Download PDF

Info

Publication number
EP3439789B1
EP3439789B1 EP17716818.4A EP17716818A EP3439789B1 EP 3439789 B1 EP3439789 B1 EP 3439789B1 EP 17716818 A EP17716818 A EP 17716818A EP 3439789 B1 EP3439789 B1 EP 3439789B1
Authority
EP
European Patent Office
Prior art keywords
nozzle
gap
pressure rotor
nozzle holder
channel
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
EP17716818.4A
Other languages
German (de)
French (fr)
Other versions
EP3439789A1 (en
Inventor
René NÖLLE
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.)
Hammelmann GmbH
Original Assignee
Hammelmann 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 Hammelmann GmbH filed Critical Hammelmann GmbH
Priority to PL17716818T priority Critical patent/PL3439789T3/en
Publication of EP3439789A1 publication Critical patent/EP3439789A1/en
Application granted granted Critical
Publication of EP3439789B1 publication Critical patent/EP3439789B1/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B05—SPRAYING OR ATOMISING IN GENERAL; APPLYING FLUENT MATERIALS TO SURFACES, IN GENERAL
    • B05B—SPRAYING APPARATUS; ATOMISING APPARATUS; NOZZLES
    • B05B3/00—Spraying or sprinkling apparatus with moving outlet elements or moving deflecting elements
    • B05B3/02—Spraying or sprinkling apparatus with moving outlet elements or moving deflecting elements with rotating elements
    • B05B3/04—Spraying or sprinkling apparatus with moving outlet elements or moving deflecting elements with rotating elements driven by the liquid or other fluent material discharged, e.g. the liquid actuating a motor before passing to the outlet
    • B05B3/06—Spraying or sprinkling apparatus with moving outlet elements or moving deflecting elements with rotating elements driven by the liquid or other fluent material discharged, e.g. the liquid actuating a motor before passing to the outlet by jet reaction, i.e. creating a spinning torque due to a tangential component of the jet
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B05—SPRAYING OR ATOMISING IN GENERAL; APPLYING FLUENT MATERIALS TO SURFACES, IN GENERAL
    • B05B—SPRAYING APPARATUS; ATOMISING APPARATUS; NOZZLES
    • B05B3/00—Spraying or sprinkling apparatus with moving outlet elements or moving deflecting elements
    • B05B3/002—Spraying or sprinkling apparatus with moving outlet elements or moving deflecting elements comprising a moving member supported by a fluid cushion
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B05—SPRAYING OR ATOMISING IN GENERAL; APPLYING FLUENT MATERIALS TO SURFACES, IN GENERAL
    • B05B—SPRAYING APPARATUS; ATOMISING APPARATUS; NOZZLES
    • B05B3/00—Spraying or sprinkling apparatus with moving outlet elements or moving deflecting elements
    • B05B3/003—Spraying or sprinkling apparatus with moving outlet elements or moving deflecting elements with braking means, e.g. friction rings designed to provide a substantially constant revolution speed
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B05—SPRAYING OR ATOMISING IN GENERAL; APPLYING FLUENT MATERIALS TO SURFACES, IN GENERAL
    • B05B—SPRAYING APPARATUS; ATOMISING APPARATUS; NOZZLES
    • B05B3/00—Spraying or sprinkling apparatus with moving outlet elements or moving deflecting elements
    • B05B3/02—Spraying or sprinkling apparatus with moving outlet elements or moving deflecting elements with rotating elements
    • B05B3/04—Spraying or sprinkling apparatus with moving outlet elements or moving deflecting elements with rotating elements driven by the liquid or other fluent material discharged, e.g. the liquid actuating a motor before passing to the outlet
    • B05B3/0409—Spraying or sprinkling apparatus with moving outlet elements or moving deflecting elements with rotating elements driven by the liquid or other fluent material discharged, e.g. the liquid actuating a motor before passing to the outlet with moving, e.g. rotating, outlet elements
    • B05B3/0418—Spraying or sprinkling apparatus with moving outlet elements or moving deflecting elements with rotating elements driven by the liquid or other fluent material discharged, e.g. the liquid actuating a motor before passing to the outlet with moving, e.g. rotating, outlet elements comprising a liquid driven rotor, e.g. a turbine
    • B05B3/0422—Spraying or sprinkling apparatus with moving outlet elements or moving deflecting elements with rotating elements driven by the liquid or other fluent material discharged, e.g. the liquid actuating a motor before passing to the outlet with moving, e.g. rotating, outlet elements comprising a liquid driven rotor, e.g. a turbine with rotating outlet elements
    • B05B3/0427—Spraying or sprinkling apparatus with moving outlet elements or moving deflecting elements with rotating elements driven by the liquid or other fluent material discharged, e.g. the liquid actuating a motor before passing to the outlet with moving, e.g. rotating, outlet elements comprising a liquid driven rotor, e.g. a turbine with rotating outlet elements the outlet elements being directly attached to the rotor or being an integral part of it

Definitions

  • the invention relates to a high-pressure rotor nozzle according to the preamble of claim 1.
  • Such a high-pressure rotary nozzle is used, for example, to remove stubborn dirt from surfaces, in particular on the inner and outer surfaces of pipes, containers or the like, with a fluid pressure of up to 4000 bar.
  • the high-pressure rotor nozzle has a nozzle holder which is rotatably mounted about an axis and which can be driven by the recoil of the pressurized water emerging from the nozzle of the nozzle holder.
  • the nozzle holder is mounted in a base body which has a central, axially aligned channel for supplying the pressurized fluid, which channel is in communication with the nozzles.
  • gap seals are arranged between the base body and the nozzle holder, as well as a leakage chamber that forms an axial bearing to absorb the recoil forces that occur during operation of the rotor nozzle, with both the gap seals and the leakage chamber being fed with leakage water and the leakage chamber being fed with the atmosphere via leakage discharge communicates.
  • Such a rotary nozzle is in the US 8 434 696 B2 disclosed.
  • At least one of the gap seals between the nozzle holder and the base body is tapered conically against the direction of the recoil force, so that the height of the gap seal increases with increasing recoil force, which leads to an increased leakage volume and thus to power losses up to, as has been shown , 50% leads, with the consequence of a correspondingly reduced cleaning efficiency in relation to the applied energy.
  • gap seals are provided, two of which are separated from the other two by leakage bores extending from the channel and a third through the leakage chamber separate, is also provided between the nozzle holder and the base body. These gap seals are assigned to the high pressure area.
  • transverse bores are provided which, starting from one of the leakage chambers, open into an axial gap with an outlet to the outside.
  • the throttling effect is achieved by narrowing the cross section of the entry area of the transverse bore when the nozzle holder moves axially, the change in cross section of the transverse bores taking place through part of the outer surface of the nozzle holder.
  • This non-linear throttle characteristic resulting from the change in the circular cross-section of the transverse bore leads to a susceptibility to vibrations and, as a result, to an unstable control behavior.
  • the invention is based on the object of further developing a high-pressure rotor nozzle of the generic type in such a way that its functionality is improved and its efficiency is increased.
  • the volume flow of the high pressure leakage, which is fed to the leakage chamber via the gap seal remains unchanged regardless of the axial position of the rotating nozzle holder.
  • the throttle gap forms a low-pressure area, for example with a pressure of approx. 20 bar, with a force equalization taking place, depending on the fluid pressure, by a self-adjusting length of the throttle gap.
  • the throttle gap preferably has a constant height, regardless of its length, for which purpose the base body, as well as the nozzle holder, which together radially delimit the throttle gap, have facing cylindrical outer surfaces, namely the base body an inner and the nozzle holder an outer outer surface.
  • the nozzle holder Due to the axially acting recoil force of the fluid emerging from the nozzles, the nozzle holder is displaced axially in the direction of the leakage chamber, the leakage liquid contained in this chamber practically forms an abutment and counteracts the recoil force.
  • the throttle gap creates a pressure in the leakage chamber that results from the leakage flowing into the leakage chamber through the assigned gap seal and the gap height of the throttle gap and is linearly dependent on the aforementioned variable length of the throttle gap, which ensures a stable setting of the pressure .
  • the volume flow of the high pressure leakage escaping from the gap seal is almost independent of the displacement position of the nozzle holder.
  • a braking device is arranged in the leakage chamber, which is part of the nozzle holder and which is designed as a fluid brake or alternatively as a magnetic brake, similar to a ship's propeller. This results in a reduction in the speed of the nozzle holder, which leads to an increase in the dwell time of the fluid jet emerging from the nozzles and thus to an improvement in the cleaning efficiency.
  • the high-pressure rotor nozzle has an outer sleeve which is dimensioned in its axial extent so that it at least largely covers the gap seal assigned to the nozzles, a circumferential annular gap being formed which is in communication with the channel supplying the fluid in the same manner as with the nozzles.
  • the fluid under high pressure is fed through the annular gap to the nozzles, the fluid being fed to the annular gap or from the annular gap to the nozzles through introduced feed channels.
  • the pressure effective in the annular gap counteracts the internal pressure of the fluid in the associated gap seal, so that the size of the gap seal remains unchanged, i.e. it is not expanded, which effectively prevents an increase in leakage.
  • This structural configuration also offers advantages in terms of manufacturing technology, since above all there is no need to make bores that are relatively long in relation to the diameter, which naturally results in significant cost savings.
  • a high-pressure rotary nozzle is shown, which in the simplest case has radial nozzles 5 exiting from the side and optionally an axial nozzle 20.
  • the rotor nozzle In its basic structure, the rotor nozzle consists of a base body 1 and a nozzle holder 2 rotatably mounted therein, which can be driven by means of the radial nozzles 5 held therein.
  • An axially extending central channel 3 is introduced into the base body 1, which starts from a connection 17 and opens opposite the fixed axial nozzle 20 held in the base body 1.
  • Liquid under high pressure (500-4000 bar) is fed via the connection 17 into the channel 3, which has transverse bores 8 through which the liquid is fed into a circumferential pocket 15 between the base body 1 and the nozzle holder 2 to the radial nozzles 5 which, moreover, run obliquely to the axis of rotation of the nozzle holder 2 towards the axial nozzle 20.
  • connection 17 In the area facing the connection 17 between the base body 1 and the nozzle holder 2, starting from the pocket 15, a first gap seal 6 is formed, via which leakage water can be guided into a leakage chamber 11, while the opposite, adjoining the pocket 15, the area associated with the axial nozzle 20 is designed as a second gap seal 7, both gap seals 6, 7 forming a high-pressure gap seal.
  • the arrangement of the connection 17 can be seen as an example. Positioning in any other suitable area is also conceivable, for example on the opposite side.
  • the throttle gap 12 in the leakage chamber 11 generates a pressure which is dependent on the amount of leakage penetrating through the first gap seal 6 into the leakage chamber 11, the constant height of the throttle gap 12 and its variable length.
  • the pressure built up in the leakage chamber 11 acts as a force against the nozzle holder 2, which is axially displaceable by recoil forces, and presses it in a direction opposite to the connection 17.
  • the nozzle holder 2 is automatically positioned in the axial direction until the recoil force of the nozzles 5 and the leakage pressure prevailing in the leakage chamber 11 are in equilibrium.
  • the nozzle holder 2 then rotates as a low-friction axial bearing without contact on the water cushion formed in the leakage chamber 11.
  • the function of the high-pressure rotary nozzle is the same for the one in the Figure 2 embodiment shown.
  • the nozzle holder 2 consists of an inner carrier sleeve 14 and an outer sleeve 19, between which an annular gap 10 is formed in the overlap area of the second gap seal 7, which is in fluid communication with the pocket 15 via feed channels 9.
  • frontal nozzles 4 are provided in the nozzle holder 2 and are inclined to its axis of rotation, through which the fluid passed through the annular gap 10 exits under high pressure, as well as from the radial nozzles 5, which are also connected to the pocket 15 and which at the same time cause the nozzle holder 2 to rotate due to the recoil forces.
  • a braking device in the form of a fluid brake 13 is arranged, which is part of the nozzle holder 2 and which is used to reduce the speed of the rotating nozzle holder 2 in order to achieve a more efficient cleaning effect.
  • the base body 1 has a circumferential casing part 16 to form the throttle gap 12, which is part of the base body 1 and the inner circumferential surface of which partially forms an outer boundary of the throttle gap 12 and the leakage chamber 11.
  • FIG Figure 3 Another example of the invention is shown in FIG Figure 3 shown, in which, however, only radial nozzles 5 are used, while an axial bearing 18 is provided on the front to support the outer sleeve 19.

Landscapes

  • Nozzles (AREA)
  • Sealing Using Fluids, Sealing Without Contact, And Removal Of Oil (AREA)

Description

Die Erfindung betrifft eine Hochdruck-Rotordüse nach dem Oberbegriff des Anspruchs 1.The invention relates to a high-pressure rotor nozzle according to the preamble of claim 1.

Eine derartige Hochdruck-Rotordüse findet beispielsweise zum Abtrag festhaftender Verschmutzungen an Oberflächen, insbesondere an Innen- und Außenflächen von Rohren, Behältern oder dergleichen Verwendung, mit einem Fluiddruck bis 4000 bar.Such a high-pressure rotary nozzle is used, for example, to remove stubborn dirt from surfaces, in particular on the inner and outer surfaces of pipes, containers or the like, with a fluid pressure of up to 4000 bar.

Die Hochdruck-Rotordüse weist einen um eine Achse drehbar gelagerten Düsenhalter auf, der durch den Rückstoß des aus Düsen des Düsenhalters austretenden Druckwassers antreibbar ist.The high-pressure rotor nozzle has a nozzle holder which is rotatably mounted about an axis and which can be driven by the recoil of the pressurized water emerging from the nozzle of the nozzle holder.

Der Düsenhalter ist in einem Grundkörper gelagert, der zur Zuführung des unter Druck stehenden Fluids einen zentralen, axial ausgerichteten Kanal aufweist, der mit den Düsen in Verbindung steht.The nozzle holder is mounted in a base body which has a central, axially aligned channel for supplying the pressurized fluid, which channel is in communication with the nozzles.

Zwischen dem Grundkörper und dem Düsenhalter sind mehrere Spaltdichtungen angeordnet, sowie eine Leckagekammer, die ein Axiallager bildet zur Aufnahme von beim Betrieb der Rotordüse auftretenden Rückstoßkräften, wobei sowohl die Spaltdichtungen wie auch die Leckagekammer mit Leckagewasser gespeist werden und die Leckagekammer über eine Leckageabfuhr mit der Atmosphäre in Verbindung steht.Several gap seals are arranged between the base body and the nozzle holder, as well as a leakage chamber that forms an axial bearing to absorb the recoil forces that occur during operation of the rotor nozzle, with both the gap seals and the leakage chamber being fed with leakage water and the leakage chamber being fed with the atmosphere via leakage discharge communicates.

Eine solche Rotordüse ist in der US 8 434 696 B2 offenbart. Dabei ist zumindest eine der Spaltdichtungen zwischen dem Düsenhalter und dem Grundkörper entgegen der Richtung der Rückstoßkraft sich verjüngend konisch ausgebildet, so dass sich die Höhe der Spaltdichtung mit zunehmender Rückstoßkraft vergrößert, was zu einem erhöhten Leckagevolumen und damit zu Leistungsverlusten bis zu, wie sich gezeigt hat, 50 % führt, mit der Folge einer im Verhältnis zur aufgebrachten Energie entsprechend reduzierten Reinigungseffizienz.Such a rotary nozzle is in the US 8 434 696 B2 disclosed. At least one of the gap seals between the nozzle holder and the base body is tapered conically against the direction of the recoil force, so that the height of the gap seal increases with increasing recoil force, which leads to an increased leakage volume and thus to power losses up to, as has been shown , 50% leads, with the consequence of a correspondingly reduced cleaning efficiency in relation to the applied energy.

Für einen Ausgleich der wirksamen Rückstoßkraft sind drei Spaltdichtungen vorgesehen, von denen zwei durch vom Kanal ausgehende Leckagebohrungen getrennt sind und eine dritte, durch die Leckagekammer von den beiden anderen getrennte, gleichfalls zwischen dem Düsenhalter und dem Grundkörper vorgesehen ist. Dabei sind diese Spaltdichtungen dem Hochdruckbereich zugeordnet.To compensate for the effective recoil force, three gap seals are provided, two of which are separated from the other two by leakage bores extending from the channel and a third through the leakage chamber separate, is also provided between the nozzle holder and the base body. These gap seals are assigned to the high pressure area.

Dies betrifft gleichermaßen eine aus der US 4 821 961 bekannte Rotordüse, bei der die Leckagekammer in einen radial ausgerichteten Niederdruckspalt übergeht, dessen Höhe, je nach rückstoßbedingter axialer Bewegung des Düsenhalters, sich gleichfalls verändert, wobei sich ein Leckageaustritt proportional zur dritten Potenz der Höhe des Niederdruckspalts ergibt. Dies bewirkt einen instabilen Ausgleich der Rückstoßkräfte, so dass auch diese Rotordüse nicht geeignet ist, den gestellten Anforderungen in dem gewünschten Umfang zu entsprechen.This also applies to one of the U.S. 4,821,961 Known rotor nozzle in which the leakage chamber merges into a radially aligned low-pressure gap, the height of which also changes depending on the axial movement of the nozzle holder caused by recoil, with a leakage output proportional to the cube of the height of the low-pressure gap. This causes an unstable compensation of the recoil forces, so that this rotary nozzle is also not suitable for meeting the requirements to the desired extent.

Eine weitere Rotordüse ist in der US 2011/0108636 A1 thematisiert. Nachteilig bei dieser bekannten Konstruktion ist zunächst die Anordnung von zwei Leckagekammern, durch die der für eine Axiallagerung relevante Leckagestrom aufgeteilt wird. Diese Ausbildung gestaltet sich hinsichtlich ihrer fertigungstechnischen Realisierung äußerst kompliziert und daher entsprechend teuer.Another rotor nozzle is in the US 2011/0108636 A1 thematized. The disadvantage of this known construction is first of all the arrangement of two leakage chambers, through which the leakage flow relevant for an axial bearing is divided. This training turns out to be extremely complicated in terms of its production technology implementation and therefore correspondingly expensive.

Überdies wird die Leckage für die Axiallagerung mittig aus dem Dichtspalt abgeführt, was eine große Leckage erfordert, mit entsprechend hohem Energieverlust und einer dadurch bedingten schlechten Effizienz der Rotordüse.In addition, the leakage for the axial bearing is discharged from the center of the sealing gap, which requires a large leakage, with a correspondingly high energy loss and the resulting poor efficiency of the rotor nozzle.

Zur Ausbildung einer Drossel sind Querbohrungen vorgesehen, die ausgehend von einer der Leckagekammern in einen axialen Spalt mit Austritt nach außen münden. Die Drosselwirkung wird dabei durch eine Querschnittsverengung des Eintrittsbereichs der Querbohrung erreicht, wenn der Düsenhalter sich axial bewegt, wobei die Querschnittsveränderung der Querbohrungen durch einen Teil der Mantelfläche des Düsenhalters erfolgt. Diese durch die Veränderung des Kreisquerschnitts der Querbohrung sich ergebende nicht lineare Drosselcharakteristik führt zu einer Schwingungsanfälligkeit und damit einhergehend einem unstabilen Regelverhalten.To form a throttle, transverse bores are provided which, starting from one of the leakage chambers, open into an axial gap with an outlet to the outside. The throttling effect is achieved by narrowing the cross section of the entry area of the transverse bore when the nozzle holder moves axially, the change in cross section of the transverse bores taking place through part of the outer surface of the nozzle holder. This non-linear throttle characteristic resulting from the change in the circular cross-section of the transverse bore leads to a susceptibility to vibrations and, as a result, to an unstable control behavior.

In der US 2006/0124362 A1 ist eine Hochdruck-Rotordüse nach dem Oberbegriff des Anspruchs 1 offenbart, bei der ein Drosselspalt in einer bestimmten Stellung geöffnet ist zwischen einer Leckagekammer und einer umfänglichen Ringnut, wobei die Breite des Drosselspaltes sich mit Verstellung des Düsenkörpers verändert.In the US 2006/0124362 A1 discloses a high-pressure rotor nozzle according to the preamble of claim 1, in which a throttle gap is opened in a certain position between a leakage chamber and a circumferential one Annular groove, the width of the throttle gap changing as the nozzle body is adjusted.

Der Erfindung liegt die Aufgabe zugrunde, eine Hochdruck-Rotordüse der gattungsgemäßen Art so weiterzuentwickeln, dass ihre Funktionsfähigkeit verbessert und ihr Wirkungsgrad erhöht wird.The invention is based on the object of further developing a high-pressure rotor nozzle of the generic type in such a way that its functionality is improved and its efficiency is increased.

Diese Aufgabe wird durch eine Hochdruck-Rotordüse gelöst, die die Merkmale des Anspruchs 1 aufweist.This object is achieved by a high-pressure rotary nozzle which has the features of claim 1.

Durch den sich an die Leckagekammer anschließenden Drosselspalt, der erfindungsgemäß einen Teilbereich des Düsenhalters umfänglich mit Spaltabstand umschließt, bleibt der Volumenstrom der Hochdruck-Leckage, die über die Spaltdichtung der Leckagekammer zugeführt wird, unabhängig von der axialen Position des rotierenden Düsenhalters unverändert.Due to the throttle gap adjoining the leakage chamber, which according to the invention surrounds a partial area of the nozzle holder circumferentially with gap spacing, the volume flow of the high pressure leakage, which is fed to the leakage chamber via the gap seal, remains unchanged regardless of the axial position of the rotating nozzle holder.

Dabei bildet der Drosselspalt einen Niederdruckbereich, beispielsweise mit einem Druck von ca. 20 bar, wobei ein Kraftausgleich, je nach Fluiddruck, durch eine sich selbst einstellende Länge des Drosselspaltes erfolgt.In this case, the throttle gap forms a low-pressure area, for example with a pressure of approx. 20 bar, with a force equalization taking place, depending on the fluid pressure, by a self-adjusting length of the throttle gap.

Bevorzugt weist der Drosselspalt, unabhängig von seiner Länge, eine gleichbleibende Höhe auf, wozu der Grundkörper, ebenso wie der Düsenhalter, die gemeinsam den Drosselspalt radial begrenzen, einander zugewandte zylindrische Mantelflächen aufweisen, und zwar der Grundkörper eine innere und der Düsenhalter eine äußere Mantelfläche.The throttle gap preferably has a constant height, regardless of its length, for which purpose the base body, as well as the nozzle holder, which together radially delimit the throttle gap, have facing cylindrical outer surfaces, namely the base body an inner and the nozzle holder an outer outer surface.

Durch die axial wirkende Rückstoßkraft des aus den Düsen austretenden Fluids wird der Düsenhalter axial in Richtung der Leckagekammer verschoben, deren beinhaltete Leckageflüssigkeit praktisch ein Widerlager bildet und der Rückstoßkraft entgegenwirkt.Due to the axially acting recoil force of the fluid emerging from the nozzles, the nozzle holder is displaced axially in the direction of the leakage chamber, the leakage liquid contained in this chamber practically forms an abutment and counteracts the recoil force.

Durch den Drosselspalt bildet sich in der Leckagekammer ein Druck aus, der sich ergibt aus der durch die zugeordnete Spaltdichtung in die Leckagekammer einfließenden Leckage und der Spalthöhe des Drosselspaltes und linear abhängig ist von der erwähnten veränderbaren Länge des Drosselspaltes, was ein stabiles Einstellverhalten des Drucks gewährleistet. Dabei ist der Volumenstrom der der Spaltdichtung entweichenden Hochdruck-Leckage nahezu unabhängig von der Verschiebeposition des Düsenhalters.The throttle gap creates a pressure in the leakage chamber that results from the leakage flowing into the leakage chamber through the assigned gap seal and the gap height of the throttle gap and is linearly dependent on the aforementioned variable length of the throttle gap, which ensures a stable setting of the pressure . The volume flow of the high pressure leakage escaping from the gap seal is almost independent of the displacement position of the nozzle holder.

Nach einem weiteren Gedanken der Erfindung ist in der Leckagekammer eine Bremseinrichtung angeordnet, die Bestandteil des Düsenhalters ist und die ähnlich einer Schiffsschraube als Fluidbremse oder alternativ als Magnetbremse ausgebildet ist. Hierdurch wird eine Drehzahlreduzierung des Düsenhalters erreicht, was zu einer Erhöhung der Verweilzeit des aus den Düsen austretenden Fluidstrahls und damit einer Verbesserung der Reinigungseffizienz führt.According to a further concept of the invention, a braking device is arranged in the leakage chamber, which is part of the nozzle holder and which is designed as a fluid brake or alternatively as a magnetic brake, similar to a ship's propeller. This results in a reduction in the speed of the nozzle holder, which leads to an increase in the dwell time of the fluid jet emerging from the nozzles and thus to an improvement in the cleaning efficiency.

Nach einem weiteren Gedanken der Erfindung weist die Hochdruck-Rotordüse eine Außenhülse auf, die in ihrer axialen Erstreckung so bemessen ist, dass sie die den Düsen zugeordnete Spaltdichtung zumindest weitgehend überdeckt, wobei ein umfänglicher Ringspalt gebildet ist, der mit dem das Fluid zuführenden Kanal ebenso flüssigkeitsoffen in Verbindung steht wie mit den Düsen. D.h., das unter Hochdruck stehende Fluid wird durch den Ringspalt zu den Düsen geführt, wobei die Zuführung des Fluids zum dem Ringspalt bzw. vom Ringspalt zu den Düsen durch eingebrachte Zuführkanäle erfolgt.According to a further concept of the invention, the high-pressure rotor nozzle has an outer sleeve which is dimensioned in its axial extent so that it at least largely covers the gap seal assigned to the nozzles, a circumferential annular gap being formed which is in communication with the channel supplying the fluid in the same manner as with the nozzles. In other words, the fluid under high pressure is fed through the annular gap to the nozzles, the fluid being fed to the annular gap or from the annular gap to the nozzles through introduced feed channels.

Der im Ringspalt wirksame Druck wirkt dem Innendruck des in der zugeordneten Spaltdichtung geführten Fluids entgegen, so dass die Spaltdichtung in ihrem Abmaß unverändert bleibt, d.h. nicht aufgeweitet wird, wodurch ein Anstieg des Leckageaustritts wirksam verhindert wird.The pressure effective in the annular gap counteracts the internal pressure of the fluid in the associated gap seal, so that the size of the gap seal remains unchanged, i.e. it is not expanded, which effectively prevents an increase in leakage.

Diese konstruktive Ausgestaltung bietet überdies fertigungstechnische Vorteile, da vor allem auf das Einbringen von im Verhältnis zum Durchmesser relativ lange Bohrungen verzichtet werden kann, woraus sich naturgemäß eine deutliche Kostenersparnis ergibt.This structural configuration also offers advantages in terms of manufacturing technology, since above all there is no need to make bores that are relatively long in relation to the diameter, which naturally results in significant cost savings.

Vorteilhafte Weiterbildungen der Erfindung sind in den Unteransprüchen gekennzeichnet.Advantageous further developments of the invention are characterized in the subclaims.

Ausführungsbeispiele der Erfindung werden nachfolgend anhand der beigefügten Zeichnungen beschrieben.Embodiments of the invention are described below with reference to the accompanying drawings.

Es zeigen:

Figuren 1 bis 3
jeweils ein Ausführungsbeispiel einer erfindungsgemäßen Hochdruck-Rotordüse in einem Längsschnitt.
Show it:
Figures 1 to 3
each an embodiment of a high-pressure rotary nozzle according to the invention in a longitudinal section.

In der Figur 1 ist eine Hochdruck-Rotordüse abgebildet, die im einfachsten Fall seitlich austretende Radialdüsen 5 aufweist und optional eine Axialdüse 20.In the Figure 1 a high-pressure rotary nozzle is shown, which in the simplest case has radial nozzles 5 exiting from the side and optionally an axial nozzle 20.

Im Grundaufbau besteht die Rotordüse aus einem Grundkörper 1 sowie einem darin drehbar gelagerten Düsenhalter 2, der mittels der darin gehaltenen Radialdüsen 5 antreibbar ist.In its basic structure, the rotor nozzle consists of a base body 1 and a nozzle holder 2 rotatably mounted therein, which can be driven by means of the radial nozzles 5 held therein.

In den Grundkörper 1 ist ein axial sich erstreckender zentrischer Kanal 3 eingebracht, der von einem Anschluss 17 ausgeht und gegenüberliegend in die fest stehende, im Grundkörper 1 gehaltene Axialdüse 20 mündet.An axially extending central channel 3 is introduced into the base body 1, which starts from a connection 17 and opens opposite the fixed axial nozzle 20 held in the base body 1.

Über den Anschluss 17 wird unter hohem Druck (500 - 4000 bar) stehende Flüssigkeit in den Kanal 3 geführt, der Querbohrungen 8 aufweist, über die die Flüssigkeit in eine umfängliche Tasche 15 zwischen dem Grundkörper 1 und dem Düsenhalter 2 zu den Radialdüsen 5 geführt wird, die im Übrigen schräg zur Drehachse des Düsenhalters 2 zur Axialdüse 20 hin geneigt verlaufen.Liquid under high pressure (500-4000 bar) is fed via the connection 17 into the channel 3, which has transverse bores 8 through which the liquid is fed into a circumferential pocket 15 between the base body 1 and the nozzle holder 2 to the radial nozzles 5 which, moreover, run obliquely to the axis of rotation of the nozzle holder 2 towards the axial nozzle 20.

In dem dem Anschluss 17 zugewandten Bereich zwischen dem Grundkörper 1 und dem Düsenhalter 2, ausgehend von der Tasche 15, ist eine erste Spaltdichtung 6 ausgebildet, über die Leckagewasser in eine Leckagekammer 11 führbar ist, während der gegenüberliegende, sich an die Tasche 15 anschließende, der Axialdüse 20 zugeordnete Bereich als zweite Spaltdichtung 7 ausgebildet ist, wobei beide Spaltdichtungen 6, 7 eine Hochdruck-Spaltdichtung bilden. Die Anordnung des Anschlusses 17 ist beispielhaft zu sehen. Denkbar ist auch eine Positionierung in jedem anderen geeigneten Bereich, bspw. an der gegenüberliegenden Seite.In the area facing the connection 17 between the base body 1 and the nozzle holder 2, starting from the pocket 15, a first gap seal 6 is formed, via which leakage water can be guided into a leakage chamber 11, while the opposite, adjoining the pocket 15, the area associated with the axial nozzle 20 is designed as a second gap seal 7, both gap seals 6, 7 forming a high-pressure gap seal. The arrangement of the connection 17 can be seen as an example. Positioning in any other suitable area is also conceivable, for example on the opposite side.

Gemäß der Erfindung geht die Leckagekammer 11, die in Funktion ein Axiallager bildet, gefüllt mit dem durch die erste Spaltdichtung 6 eintretenden Fluids in mindestens einen, den Düsenhalter 2 in einem Teilbereich umfänglich umschließenden, achsparallel zum Kanal 3 verlaufenden Drosselspalt 12 über, der zur Atmosphäre hin offen ist, wobei der Fluiddruck durch den Drosselspalt 12 stark reduziert wird.According to the invention, the leakage chamber 11, which in function forms an axial bearing, filled with the fluid entering through the first gap seal 6, merges into at least one throttle gap 12, which circumferentially surrounds the nozzle holder 2 in a partial area, runs axially parallel to the channel 3, and which to the atmosphere is open, the fluid pressure being greatly reduced by the throttle gap 12.

In Funktion wird durch den Drosselspalt 12 in der Leckagekammer 11 ein Druck erzeugt, der abhängig ist von der durch die erste Spaltdichtung 6 in die Leckagekammer 11 eindringende Leckagemenge, der gleichbleibenden Höhe des Drosselspalts 12 sowie von dessen variabler Länge.In operation, the throttle gap 12 in the leakage chamber 11 generates a pressure which is dependent on the amount of leakage penetrating through the first gap seal 6 into the leakage chamber 11, the constant height of the throttle gap 12 and its variable length.

Der dabei in der Leckagekammer 11 aufgebaute Druck wirkt als Kraft gegen den durch Rückstoßkräfte axial verschiebbaren Düsenhalter 2 und drückt diesen in eine zum Anschluss 17 entgegengesetzte Richtung. Je weiter sich dabei der Düsenhalter 2 bewegt, desto kürzer wird die Länge des Drosselspaltes 12, was wiederum den Druck in der Leckagekammer 11 senkt und damit die auf den Düsenhalter 2 wirkende Kraft reduziert. Dadurch erfolgt eine automatische Positionierung des Düsenhalters 2 in axialer Richtung, bis die Rückstoßkraft der Düsen 5 und der in der Leckagekammer 11 herrschende Leckagedruck im Gleichgewicht sind. Der Düsenhalter 2 rotiert dann als reibungsarmes Axiallager berührungslos auf dem in der Leckagekammer 11 gebildeten Wasserpolster.The pressure built up in the leakage chamber 11 acts as a force against the nozzle holder 2, which is axially displaceable by recoil forces, and presses it in a direction opposite to the connection 17. The further the nozzle holder 2 moves, the shorter the length of the throttle gap 12 becomes, which in turn lowers the pressure in the leakage chamber 11 and thus reduces the force acting on the nozzle holder 2. As a result, the nozzle holder 2 is automatically positioned in the axial direction until the recoil force of the nozzles 5 and the leakage pressure prevailing in the leakage chamber 11 are in equilibrium. The nozzle holder 2 then rotates as a low-friction axial bearing without contact on the water cushion formed in the leakage chamber 11.

Funktionsgleich stellt sich auch die Hochdruck-Rotordüse bei dem in der Figur 2 gezeigten Ausführungsbeispiel dar.The function of the high-pressure rotary nozzle is the same for the one in the Figure 2 embodiment shown.

Hierbei besteht der Düsenhalter 2 aus einer inneren Trägerhülse 14 und einer Außenhülse 19, zwischen denen im Überdeckungsbereich der zweiten Spaltdichtung 7 ein Ringspalt 10 ausgebildet ist, der über Zuführkanäle 9 mit der Tasche 15 flüssigkeitsoffen in Verbindung steht.In this case, the nozzle holder 2 consists of an inner carrier sleeve 14 and an outer sleeve 19, between which an annular gap 10 is formed in the overlap area of the second gap seal 7, which is in fluid communication with the pocket 15 via feed channels 9.

Am gegenüberliegenden Ende des Ringspalts 10 sind im Düsenhalter 2 zu dessen Drehachse geneigt verlaufend Frontaldüsen 4 vorgesehen, über die das durch den Ringspalt 10 geleitete Fluid unter hohem Druck austritt, ebenso wie aus den Radialdüsen 5, die ebenfalls mit der Tasche 15 in Verbindung stehen und die gleichzeitig aufgrund der Rückstoßkräfte eine Rotation des Düsenhalters 2 bewirken.At the opposite end of the annular gap 10, frontal nozzles 4 are provided in the nozzle holder 2 and are inclined to its axis of rotation, through which the fluid passed through the annular gap 10 exits under high pressure, as well as from the radial nozzles 5, which are also connected to the pocket 15 and which at the same time cause the nozzle holder 2 to rotate due to the recoil forces.

Da das Leckagefluid in der zweiten Spaltdichtung 7 in etwa unter gleichem Druck steht wie das im Ringspalt 10 geführte Fluid, wird ein Gegendruck wirksam, durch den ein Aufweiten der Spaltdichtung 7 wirksam verhindert wird.Since the leakage fluid in the second gap seal 7 is under approximately the same pressure as the fluid guided in the annular gap 10, a counterpressure is effective, which effectively prevents the gap seal 7 from expanding.

Im Bereich der Leckagekammer 11 ist eine Bremseinrichtung in Form einer Fluidbremse 13 angeordnet, die Bestandteil des Düsenhalters 2 ist und die der Drehzahlsenkung des rotierenden Düsenhalters 2 dient, um so eine effizientere Reinigungswirkung zu erreichen.In the area of the leakage chamber 11, a braking device in the form of a fluid brake 13 is arranged, which is part of the nozzle holder 2 and which is used to reduce the speed of the rotating nozzle holder 2 in order to achieve a more efficient cleaning effect.

Im Übrigen weist der Grundkörper 1 zur Ausbildung des Drosselspalts 12 ein umfängliches Mantelteil 16 auf, das Bestandteil des Grundkörpers 1 ist und dessen innere Mantelfläche teilweise eine äußere Begrenzung des Drosselspalts 12 sowie der Leckagekammer 11 bildet.For the rest, the base body 1 has a circumferential casing part 16 to form the throttle gap 12, which is part of the base body 1 and the inner circumferential surface of which partially forms an outer boundary of the throttle gap 12 and the leakage chamber 11.

Ein weiteres Beispiel der Erfindung ist in der Figur 3 abgebildet, bei der allerdings lediglich Radialdüsen 5 zum Einsatz kommen, während frontseitig ein Axiallager 18 zur Abstützung der Außenhülse 19 vorgesehen ist.Another example of the invention is shown in FIG Figure 3 shown, in which, however, only radial nozzles 5 are used, while an axial bearing 18 is provided on the front to support the outer sleeve 19.

Bei dieser Ausführungsvariante kann zur Drehzahlreduzierung des Düsenhalters 2 anstelle einer Fluidbremse 13 eine Magnetbremse 13' vorgesehen sein, die lediglich zur Verdeutlichung dargestellt ist.In this embodiment variant, instead of a fluid brake 13, a magnetic brake 13 'can be provided to reduce the speed of the nozzle holder 2, which is only shown for the sake of clarity.

BezugszeichenlisteList of reference symbols

11
GrundkörperBase body
22
DüsenhalterNozzle holder
33
Kanalchannel
44th
FrontaldüseFrontal nozzle
55
RadialdüseRadial nozzle
66th
erste Spaltdichtungfirst gap seal
77th
zweite Spaltdichtungsecond gap seal
88th
QuerbohrungCross hole
99
ZuführkanalFeed channel
1010
RingspaltAnnular gap
1111
LeckagekammerLeakage chamber
1212th
DrosselspaltThrottle gap
1313th
FluidbremseFluid brake
13'13 '
MagnetbremseMagnetic brake
1414th
TrägerhülseCarrier sleeve
1515th
Taschebag
1616
MantelteilShell part
1717th
Anschlussconnection
1818th
AxiallagerThrust bearings
1919th
AußenhülseOuter sleeve
2020th
AxialdüseAxial nozzle

Claims (12)

  1. High-pressure rotor nozzle, comprising a main body (1) having a channel (3) for supplying a liquid under high pressure, a nozzle holder (2) rotatably drivable by a hydraulically generated torque and having at least one nozzle (4, 5) which is in connection in a liquid-open manner with the channel (3) and causes an axial recoil in operation, wherein a leakage chamber (11) forming a hydraulic axial bearing in operation is provided between the main body (1) and the nozzle holder (2) that can be axially adjusted in relation to the same in a recoil-dependent manner, with said leakage chamber being connected to a first gap seal (6), guiding a leakage fluid, between the main body (1) and the nozzle holder (2), characterized in that the leakage chamber (11) changes into at least one throttle gap (12) circumferentially surrounding the nozzle holder (2) in an axial sub-region and varying in the axial extension thereof according to the movement path of the nozzle holder (2), wherein the throttle gap (12) remains the same height over the axial length thereof.
  2. High-pressure rotor nozzle according to claim 1, characterized in that the throttle gap (12) is open to the atmosphere.
  3. High-pressure rotor nozzle according to claim 1 or 2, characterized in that the throttle gap (12) is formed between the main body (1) and the nozzle holder (2).
  4. High-pressure rotor nozzle according to one of the preceding claims, characterized in that the throttle gap (12) runs parallel to the axis of the channel (3).
  5. High-pressure rotor nozzle according to one of the preceding claims, characterized in that the nozzle holder (2) has a speed-reducing braking device, preferably a fluid brake (13) or a magnetic brake (13 ').
  6. High-pressure rotor nozzle according to one of the preceding claims, characterized in that a second gap seal (7) is provided between the main body (1) and the nozzle holder (2) downstream of the first gap seal (6) in the axial direction, starting from the leakage chamber (11), wherein between the two gap seals (6, 7) a preferably circumferential pocket (15) is formed, said pocket forming a pressure chamber and being liquid-open to the channel (3) and into which the at least one radial nozzle (5) opens.
  7. High-pressure rotor nozzle according to claim 6, characterized in that the nozzle holder (2) has a concentric annular gap (10) which at least partially covers the smaller-diameter gap seal (7) in the axial direction.
  8. High-pressure rotor nozzle according to claim 7, characterized in that the annular gap (10) is in liquid-open communication on the one hand with the channel (3) and on the other hand with at least one nozzle (4).
  9. High-pressure rotor nozzle according to claim 7, characterized in that the annular gap (10) is connected via at least one feed channel (9) to the channel (3).
  10. High-pressure rotor nozzle according to one of the preceding claims, characterized in that the nozzle holder (2) has a support sleeve (14) and an outer sleeve (19) encompassing the latter and connected thereto, wherein the annular channel (10) is delimited by the outer jacket surface of the support sleeve (14) and the inner jacket surface of the outer sleeve (19).
  11. High-pressure rotor nozzle according to claim 9 or 10, characterized in that the feed channel (9) and the at least one nozzle (4, 5) are arranged in the support sleeve (14).
  12. High-pressure rotor nozzle according to claim 6, characterized in that the mutually facing jacket surfaces of the nozzle holder (2) and of the main body (1) which delimit the gap seals (6, 7) are cylindrical.
EP17716818.4A 2016-04-07 2017-04-05 High-pressure rotor nozzle Active EP3439789B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PL17716818T PL3439789T3 (en) 2016-04-07 2017-04-05 High-pressure rotor nozzle

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102016106376.2A DE102016106376A1 (en) 2016-04-07 2016-04-07 High-pressure rotor nozzle
PCT/EP2017/058052 WO2017174622A1 (en) 2016-04-07 2017-04-05 High-pressure rotor nozzle

Publications (2)

Publication Number Publication Date
EP3439789A1 EP3439789A1 (en) 2019-02-13
EP3439789B1 true EP3439789B1 (en) 2021-05-26

Family

ID=58536945

Family Applications (1)

Application Number Title Priority Date Filing Date
EP17716818.4A Active EP3439789B1 (en) 2016-04-07 2017-04-05 High-pressure rotor nozzle

Country Status (7)

Country Link
US (1) US11077453B2 (en)
EP (1) EP3439789B1 (en)
DE (1) DE102016106376A1 (en)
DK (1) DK3439789T3 (en)
ES (1) ES2883625T3 (en)
PL (1) PL3439789T3 (en)
WO (1) WO2017174622A1 (en)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH714354A2 (en) * 2017-11-17 2019-05-31 Mvt Micro Verschleiss Technik Ag A fluid jet nozzle device, method of manufacturing a nozzle device, and kit comprising a rotor and a hollow needle for a nozzle device.
CN114526163B (en) * 2022-04-24 2022-07-26 中国航发四川燃气涡轮研究院 Lubricating oil nozzle device and aircraft engine

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4821961A (en) 1988-03-31 1989-04-18 Nlb Corp. Self-rotating nozzle
DE4001335C1 (en) * 1990-01-18 1991-01-31 Paul Hammelmann Maschinenfabrik Gmbh, 4740 Oelde, De High-pressure plunger pump - incorporates adjustable sleeve and disc-types inlet valve
US5141158A (en) * 1991-04-24 1992-08-25 Halliburton Company Eddy current braked spinning jet nozzle
DE19711837A1 (en) * 1997-03-21 1998-09-24 Hammelmann Paul Maschf Nozzle head with a drivable nozzle holder which is rotatably mounted about a longitudinal axis
DE10029920C2 (en) * 2000-06-17 2002-07-11 Horst Goetz Gmbh & Co Nozzle-like work tool for cleaning pipes
CA2592770C (en) * 2004-12-30 2013-07-09 Tempress Technologies, Inc. Floating head reaction turbine rotor with improved jet quality
US8016210B2 (en) 2005-08-19 2011-09-13 Balanced Body, Inc. Self regulating fluid bearing high pressure rotary nozzle with balanced thrust force
DE202008002597U1 (en) * 2007-02-26 2008-04-30 Falch Hochdruckstrahlsysteme Gmbh Rotary nozzle
US8298349B2 (en) 2009-08-13 2012-10-30 Nlb Corp. Rotating fluid nozzle for tube cleaning system
US8544768B2 (en) * 2009-11-10 2013-10-01 Stoneage, Inc. Self regulating fluid bearing high pressure rotary nozzle with balanced thrust force
DE202011109850U1 (en) * 2011-04-06 2012-08-08 Lechler Gmbh Rotating nozzle arrangement

Non-Patent Citations (1)

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

Also Published As

Publication number Publication date
PL3439789T3 (en) 2021-09-27
US11077453B2 (en) 2021-08-03
ES2883625T3 (en) 2021-12-09
DE102016106376A1 (en) 2017-10-12
EP3439789A1 (en) 2019-02-13
DK3439789T3 (en) 2021-08-09
WO2017174622A1 (en) 2017-10-12
US20200222924A1 (en) 2020-07-16

Similar Documents

Publication Publication Date Title
EP1069362B1 (en) Rotatable connection for alternate mediums
DE2356817C3 (en) Self-pressure generating radial plain bearing
EP2403682B1 (en) Spindle comprising a lance
DE2843658A1 (en) OIL FILM STORAGE
DE2653504A1 (en) ARRANGEMENT FOR REDUCING OIL LEAK OF A UNIT WITH A PIVOT BEARING
WO2013167124A2 (en) Piston/cylinder unit
EP0411427B1 (en) Roll for heat and pressure treatment of web material
EP3199815B1 (en) Centrifugal pump
EP3439789B1 (en) High-pressure rotor nozzle
CH512019A (en) Hydrostatic radial and axial plain bearings for shaft
DE60104329T2 (en) SHAFT SEAL
DE2351222C3 (en) Mold clamping device for an injection molding machine with a double-acting hydraulic lock cylinder
DE1812251A1 (en) Cell or rotary vane pump
WO2000034664A1 (en) Releasable check valve for very high system pressures
DE3930147C2 (en)
DE4139506C2 (en) Rotary slide valve for power steering
DE2326417C3 (en) Hydraulic cylinder with end position cushioning
CH638590A5 (en) HYDROSTATIC PISTON MACHINE.
EP4072737A1 (en) Cleaning apparatus
DE1003040B (en) Axial piston pump or motor with rotating cylinder drum
DE3734926C2 (en)
WO2011051233A2 (en) Rudder engine
EP1270955B1 (en) Means for frictionally applying a booster piston to a piston rod of a fluid power cylinder
DE102010047633B4 (en) Multi-part piston for a cylinder arrangement
DE3722436A1 (en) HYDROSTATIC SEAL

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: 20180831

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

DAV Request for validation of the european patent (deleted)
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

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: 20201001

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

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

Free format text: STATUS: REQUEST FOR EXAMINATION WAS MADE

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

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

Free format text: STATUS: GRANT OF PATENT IS INTENDED

INTC Intention to grant announced (deleted)
GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

INTG Intention to grant announced

Effective date: 20210219

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: AT

Ref legal event code: REF

Ref document number: 1395687

Country of ref document: AT

Kind code of ref document: T

Effective date: 20210615

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 502017010460

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

REG Reference to a national code

Ref country code: DK

Ref legal event code: T3

Effective date: 20210805

REG Reference to a national code

Ref country code: NL

Ref legal event code: FP

REG Reference to a national code

Ref country code: SE

Ref legal event code: TRGR

REG Reference to a national code

Ref country code: LT

Ref legal event code: MG9D

REG Reference to a national code

Ref country code: NO

Ref legal event code: T2

Effective date: 20210526

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

Ref country code: LT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210526

Ref country code: FI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210526

Ref country code: BG

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210826

Ref country code: HR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210526

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

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210827

Ref country code: LV

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210526

Ref country code: IS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210926

Ref country code: RS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210526

Ref country code: PT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210927

REG Reference to a national code

Ref country code: ES

Ref legal event code: FG2A

Ref document number: 2883625

Country of ref document: ES

Kind code of ref document: T3

Effective date: 20211209

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

Ref country code: RO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210526

Ref country code: EE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210526

Ref country code: SK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210526

Ref country code: SM

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210526

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 502017010460

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

26N No opposition filed

Effective date: 20220301

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

Ref country code: IS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210926

Ref country code: AL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210526

REG Reference to a national code

Ref country code: BE

Ref legal event code: MM

Effective date: 20220430

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

Ref country code: MC

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210526

Ref country code: LU

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

Effective date: 20220405

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

Ref country code: BE

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

Effective date: 20220430

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

Ref country code: IE

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

Effective date: 20220405

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

Ref country code: HU

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT; INVALID AB INITIO

Effective date: 20170405

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

Ref country code: MK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210526

Ref country code: CY

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210526

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

Ref country code: CZ

Payment date: 20240318

Year of fee payment: 8

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

Ref country code: NL

Payment date: 20240422

Year of fee payment: 8

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

Ref country code: SE

Payment date: 20240318

Year of fee payment: 8

Ref country code: PL

Payment date: 20240314

Year of fee payment: 8

Ref country code: NO

Payment date: 20240318

Year of fee payment: 8

Ref country code: DK

Payment date: 20240314

Year of fee payment: 8

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

Ref country code: TR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210526

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

Ref country code: GB

Payment date: 20240411

Year of fee payment: 8

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

Ref country code: DE

Payment date: 20240524

Year of fee payment: 8

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

Ref country code: CH

Payment date: 20240501

Year of fee payment: 8

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

Ref country code: ES

Payment date: 20240517

Year of fee payment: 8

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

Ref country code: AT

Payment date: 20240422

Year of fee payment: 8

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

Ref country code: IT

Payment date: 20240430

Year of fee payment: 8

Ref country code: FR

Payment date: 20240411

Year of fee payment: 8

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

Ref country code: MT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210526