EP3303845B1 - Ensemble de pompes à amorçage automatique - Google Patents

Ensemble de pompes à amorçage automatique Download PDF

Info

Publication number
EP3303845B1
EP3303845B1 EP16726880.4A EP16726880A EP3303845B1 EP 3303845 B1 EP3303845 B1 EP 3303845B1 EP 16726880 A EP16726880 A EP 16726880A EP 3303845 B1 EP3303845 B1 EP 3303845B1
Authority
EP
European Patent Office
Prior art keywords
annular channel
self
bulge
housing
longitudinal axis
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
EP16726880.4A
Other languages
German (de)
English (en)
Other versions
EP3303845A1 (fr
Inventor
Simon Anderson
Stephan Dirks
Christoph Wabnitz
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.)
GEA Tuchenhagen GmbH
Original Assignee
GEA Tuchenhagen 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 GEA Tuchenhagen GmbH filed Critical GEA Tuchenhagen GmbH
Priority to PL16726880T priority Critical patent/PL3303845T3/pl
Publication of EP3303845A1 publication Critical patent/EP3303845A1/fr
Application granted granted Critical
Publication of EP3303845B1 publication Critical patent/EP3303845B1/fr
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
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D9/00—Priming; Preventing vapour lock
    • F04D9/004—Priming of not self-priming pumps
    • F04D9/005—Priming of not self-priming pumps by adducting or recycling liquid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/426—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for liquid pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/426—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for liquid pumps
    • F04D29/428—Discharge tongues
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D9/00—Priming; Preventing vapour lock
    • F04D9/04—Priming; Preventing vapour lock using priming pumps; using booster pumps to prevent vapour-lock
    • F04D9/041—Priming; Preventing vapour lock using priming pumps; using booster pumps to prevent vapour-lock the priming pump having evacuating action
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2250/00—Geometry
    • F05D2250/50—Inlet or outlet
    • F05D2250/52—Outlet

Definitions

  • the invention relates to a self-priming pump aggregation, which is a series connection of a working as a rotary positive displacement liquid ring pump and a normal suction centrifugal pump, according to the preamble of claim 1.
  • the invention relates in this context, in particular the liquid-carrying return line, the annular channel of the centrifugal pump with the interior of the positive displacement pump connects, wherein the return line opens out on the annular channel side via the first connection opening, which is arranged in the laterally extending to the impeller plane lateral boundary surface of the annular channel.
  • a self-priming pump aggregation of the generic type is from the DE 10 2007 032 228 A1 and from the nachannostien WO 2009/007075 A1 known.
  • this known pump aggregation necessary for the suction of a liquid evacuation of the suction-side portion of the normal-suction centrifugal pump is accomplished by the centrifugal pump upstream rotary displacement pump.
  • the rotating positive displacement pump embodied as a so-called liquid ring pump is, with sufficient liquid charge in its housing, capable of delivering gas and thus can evacuate an upstream process arrangement and suck and convey liquid or a two-phase flow consisting of liquid and gas.
  • the centrifugal pump essentially takes over the delivery of the liquid or possibly within limits of the two-phase flow in accordance with its delivery characteristic influenced by the flow losses in the upstream positive displacement pump.
  • the positive displacement pump requires a permanent readiness for operation before evacuation, which may become necessary, of the process arrangement connected on the suction side always the mentioned sufficient liquid template, so that the feed chamber formed by its screw conveyor can ensure the necessary gas transport if necessary.
  • this liquid feed is additionally fed and maintained by a return line for fluid which establishes a connection between a pressure-side interior of the centrifugal pump arranged downstream of the impeller, as seen in the flow direction (a first connection point or first connection opening). and on the other hand the interior of the housing or the suction nozzle of the positive displacement pump or the suction line connected to the latter (a second connection point or second connection opening).
  • the fluid delivery in the return line is necessarily an image of what is available at the first connection point or first connection opening of the return line on the pressure-side interior to each fluid.
  • the prior art is known to connect the return line to the annular channel, which is an integral part of the pressure-side interior, and the relevant first connection opening at a radially or approximately radially oriented lateral boundary surface, which is part of the rear housing part and the annular channel in the axial direction in shape an annular surface frontally limited to provide.
  • this annular channel which may be formed as a spiral annular channel or as a vane-less annular space with a constant passage cross-section, the flow is delayed, resulting in a part of the kinetic energy the flow leaving the impeller is converted to static pressure so that the static pressure in the annular duct increases overall.
  • the static pressure is, in sufficient height compared to the static pressure in the positive displacement pump, needed for fluid transport in the return line.
  • the arrangement of the first connection opening on the above-described radial or approximately radially oriented lateral boundary surface makes use of the fact that preferably at least not too critical two-phase flow, liquid is in this area and can be "harvested” there, since gas components in axial Direction seen, rearmost, frontal wall area of the annular channel or shovel-free annulus avoid if possible.
  • a longitudinal axis of the first connection opening or the return line is preferably arranged centrally or approximately centrally relative to the radial extension region of the lateral boundary surface.
  • a self-priming centrifugal pump is known in which a control valve in the return line is arranged to improve the flow to and in the return line.
  • a separate air separation chamber is known to reduce turbulence during the self-priming phase.
  • a self-priming centrifugal pump is known in which a reduction in fluid velocity is to be achieved by means of a diffuser provided with a return channel and associated deflector.
  • the invention proceeds in a manner known per se from a self-priming pump aggregation, which constitutes a series connection of a liquid-ring pump operating as a rotating positive-displacement pump and a normal-suction centrifugal pump.
  • the centrifugal pump has a rotatably mounted shaft with an impeller in a housing provided with an inlet opening and a pressure port.
  • the housing consists preferably, seen in the flow direction, of a front and a rear housing part, and it forms, in addition to the impeller receiving area, an annular channel, the area of the impeller radially outside either in the impeller level and / or in at least one encloses axially adjacent area.
  • the inlet opening is arranged coaxially on the front housing part, wherein an interior bounded by a housing jacket of the displacement pump is connected via the inlet opening to a suction-side interior of the centrifugal pump.
  • a screw conveyor is arranged, which is fastened on the shaft passing through the impeller and in the housing shell.
  • a fluid-carrying return line is provided, which connects the annular channel with the interior, wherein the return line opens out on the annular channel side via a first connection opening, which is arranged in a lateral boundary surface of the annular channel extending laterally relative to the impeller plane.
  • the first connection opening has a bulge which encloses a sectoral axis along a longitudinal axis of the first connection opening.
  • the latter is one-sided and the center of Pump aggregation oriented towards, and it constantly widens the first port to the annular channel out directly or indirectly.
  • the bulge with a transition surface in the lateral boundary surface or in an adjoining the latter inner peripheral wall of the annular channel is continuous.
  • the measure according to the invention leads to a reduction of the flow vortices in the return line.
  • This reduced turbulence which can be detected especially in the pipe section of the return line directly adjoining the inlet region, reduces the flow losses and the homogenization effect in the return line (mixing, division and distribution of the gas admixtures into the liquid), whereby the suction time is further reduced and the supply of the Positive displacement pump is further improved.
  • the features essential to the invention come into their own in a special way.
  • This embodiment provides that the front housing part has the outer peripheral wall of the annular channel forming, circular, substantially cylindrically extending outer annular channel housing wall and the latter emerging from the discharge nozzle, which is connected tangentially to the outer annular channel housing wall.
  • the rear housing part has the inner circumferential wall of the annular channel forming inner annular channel housing wall, which preferably runs parallel to the outer annular channel housing wall.
  • the annular channel is formed in an axially adjacent region of the impeller plane, which, viewed in the flow direction, lies behind the impeller and exclusively outside the region covered by the impeller.
  • the lateral boundary surface is part of the rear housing part, which is preferably aligned radially and the annular channel bounded in the axial direction as the rear, frontal wall region.
  • the inflow conditions to and the inlet conditions in the first port and thus in the return line further improved and the recirculation flow is amplified and sustainably generated when, as provided, the first port to the annular channel initially expanded in the form of a countersink.
  • the bulge according to the invention engages in the axial direction into the countersink or through the countersink, resulting in a continuous cross-sectional widening of the described area towards the annular channel. If the bulge engages only in the countersink, then only the countersink extends to the annular channel out.
  • the countersink can be completely or even partially covered in the radial direction of the bulge.
  • the countersink may be, for example, conical, conical, conical in the broadest sense or tulip-shaped. It is preferably formed axially symmetrical and coaxial with the longitudinal axis of the first connection opening, which significantly simplifies their cutting shaping.
  • a further improvement of the inflow conditions to and the inlet conditions in the first connection opening and thus in the return line turns when, as another proposal provides, the longitudinal axis of the first connection opening is eccentrically offset from the radial extension region of the lateral boundary surface and offset radially inwards ,
  • This measure makes a further contribution to the reinforcement and sustainable generation of the recirculation flow already described above. It is in the context of the above-defined radial offset of the longitudinal axis also advantageous if it is spaced apart from the annular channel radially inner side bounding inner peripheral wall to a half inner diameter of the return line.
  • a preferred embodiment of the invention provides that the longitudinal axis of the first connection opening is perpendicular to and at the point of contact of the tangent to the lateral boundary surface. This embodiment then creates particularly simple geometric conditions with regard to the connection of the return line to the annular channel when the lateral boundary surface of the annular channel is radially aligned.
  • a further proposal provides that an axis of symmetry of the bulge forms an angle with the longitudinal axis of the first connection opening perpendicular to the lateral boundary surface, the axial extension direction of the bulge being oriented radially inward.
  • This refinement further improves the inflow conditions for and the inlet conditions into the first connection opening and thus into the return line, because it counteracts a contraction of the flow in the region of the first connection opening by additional expansion of the first connection opening.
  • the steady transition from the bulge in the adjacent inner peripheral wall of the annular channel is realized virtually without additional shaping measure.
  • a further embodiment provides that the longitudinal axis of the first connection opening, viewed in the direction of flow through the return line, is oriented radially inwards towards the center of the pump aggregation.
  • This embodiment is applicable to any geometric shape of the annular channel, even on parallel circumferential walls in conjunction with a radially oriented lateral Limiting surface. It improves in each case the bumpless entry of the flow in the return line, because the described inclination of the longitudinal axis causes a similar fluidic effect as the above-described inclination of the symmetry axis of the bulge.
  • first connection opening seen in a cross-sectional plane perpendicular to the rotation axis of the pump aggregation, is positioned with respect to the discharge nozzle in such a way that a first arrangement plane passing through a radial directional vector, on the one hand through the center of the first connection opening and on the other hand passes through the axis of rotation of the pump aggregate, is penetrated perpendicularly by the longitudinal axis of the pressure port.
  • the first connection opening is positioned in relation to the pressure connection such that a second arrangement plane passing through a radial directional vector passes through the center of the first connection opening on the one hand and through an axial one on the other Symmetryeachse the housing shell extends, is penetrated perpendicularly by the longitudinal axis of the pressure port.
  • the respectively defined position of the first connection opening means that a point in the annular channel is selected immediately before entry of the flow in the discharge nozzle of the centrifugal pump, at which the maximum possible static pressure within the housing of the centrifugal pump is present. It is understood that the first connection opening can also be arranged between the first and the second arrangement level or in a narrow sectoral area in each case, viewed in the circumferential direction, adjacent to these arrangement areas, without leaving the invention.
  • a self-priming pump aggregation 1 ( FIGS. 1 to 3 ) is from a normal suction centrifugal pump (centrifugal pump) 2 and one of these, seen in the flow direction, upstream rotary positive displacement pump 20, which is designed in the embodiment as a so-called. Liquid ring pump is formed.
  • the displacement pump 20 is on the housing side of a housing shell 20.1 ( Figures 2 . 1 ) and a housing cover 20.2 with a centrally arranged on the latter suction nozzle 20.2a limited, wherein the housing shell 20.1 is fixedly connected at its end remote from the housing cover 20.2 end with a front housing part 2.1 of the centrifugal pump 2.
  • An axial axis of symmetry a 2 of the housing shell 20.1 is opposite a rotational axis a 1 of the pump aggregation 1 (see FIGS. 1 and 3 ), based on the drawing position of the pump aggregation 1, which also corresponds to the usual installation position, offset by a vertical eccentricity e down.
  • the positive displacement pump 20 screw conveyor 21 which is arranged on a shaft extension 8b of an impeller 4 of the centrifugal pump 2 bearing shaft 8 to this vertical eccentricity e within the housing shell 20.1 moved upwards.
  • the shaft extension 8b adjoins a hub 8a of the shaft 8, wherein on the hub 8a, the impeller 4 is fixed, and it engages through the front housing part 2.1 and in the housing shell 20.1 a.
  • An inner space 20.3 bounded on the inside by the housing jacket 20.1, the housing cover 20.2 and the front housing part 2.1 is provided via an inlet opening 2.1b (2.1b ) arranged concentrically in the front housing part 2.1 and thus concentrically with the axis of rotation a1.
  • FIG. 2 With a suction-side interior 2.1c of the centrifugal pump 2 fluidly connected.
  • the structure of the centrifugal pump 2 is for example from the DE 103 14 425 B4 known.
  • A consisting of the front 2.1 and a rear housing part 2.2 housing 2.1 / 2.2 of the centrifugal pump 2 is mounted on a mounting flange 7 on a flying motor 6 ( FIGS. 1 and 2 ).
  • the inlet opening 2.1b is centrally formed and at its periphery and there tangentially opening out a discharge nozzle 5 is connected, which ends via a conical extension 5a in a connecting piece 5b.
  • the front and the rear housing part 2.1, 2.2 are adapted to the impeller 4 in their radial extension region, each with a narrow annular gap.
  • On the annular circumferential impeller outlet cross-section is followed by a blade-less annular space 3a on the outside, which is limited in the radial direction initially on both sides of the front and the rear housing part 2.1, 2.2 a piece and then outside bounded by an unnamed transition surface of the front housing part 2.1.
  • This transition surface is then continued in an outer annular channel housing wall 2.1 a, wherein this at least on the inside, for example, has the shape of a cylinder jacket, ie a constant radius of curvature, an outer radius, has ( FIG. 3 ).
  • the rear housing part 2.2 is formed in the region of the impeller 4 as a preferably radially extending disk.
  • annular channel 3 * which can be designed as a spiral annular channel 3 ** in the case of a continuously changing passage cross section (variable local radius of curvature). Nevertheless, with the arrangement shown, an annular channel 3 * with a passage cross section which is constant over the circumference can also be realized.
  • the (spiral) annular channel (3 **) 3 * joins laterally to the blade-less annular space 3a; together they form a pressure-side interior 3 of the centrifugal pump second
  • FIG. 3 shows by way of example how the spiral annular channel 3 **, seen over the circumference, steadily widened.
  • the passage cross section of the spiral annular channel 3 ** increases steadily from a minimum cross-section to a point where in FIG. 3 the horizontal center line intersecting with the axis of rotation a 1 forms a vertical with the longitudinal axis of the pressure port 5.
  • the inner annular channel housing wall 2.2a is continuously curved.
  • the inner annular channel housing wall 2.2a may also be formed in a different form, for example continuously curved.
  • the outer axial boundary of the (spiral) annular channel (3 **) 3 * is realized via a laterally to the inner annular channel housing wall 2.2a, from the axis of rotation a 1 in the radial direction, in a lateral to the impeller plane extending lateral boundary surface 2.2b, which is part of the rear housing part 2.2 ( FIG. 2 ).
  • the lateral boundary surface 2.2b is preferably oriented radially and bounds the annular channel 3 *, 3 ** in the axial direction as the rearmost, frontal wall region.
  • the lateral boundary surface 2.2b preferably continues radially outward over the outermost radial extent of the outer annular channel housing wall 2.1a ( FIG. FIG. 2 ).
  • the outer annular channel housing wall 2.1a is adjoined by an unspecified, radially oriented annular surface which corresponds to the lateral boundary surface 2.2b and is detachably connected thereto, which on the outside comprises the lateral boundary surface 2.2b.
  • the two radially oriented aforementioned surfaces are sealed against each other on the annular channel side (housing seal 28; FIG. 6 ), and they have a plurality of distributed through their circumference, mutually corresponding through holes through which the front and the rear housing part 2.1, 2.2 are preferably screwed together.
  • a return line 9 ( Figures 2 . 1 . 3 ) is connected on the centrifugal pump side via a first connection opening 9a to the annular channel 3 * or the spiral annular channel 3 **.
  • a preferred arrangement point for the first connection opening 9a is the radially oriented lateral boundary surface 2.2b, which is part of the rear housing part 2.2 and the annular channel 3 *, 3 ** frontally limited in the radial direction, ie the annular channel 3 *, 3 ** flows there into the first connection opening 9a.
  • first connection point 9a is positioned with respect to the discharge nozzle 5 in such a way that a first arrangement plane E (see FIG. 3 ), which passes through a radial direction vector which extends on the one hand through the center of the first connection opening 9a and on the other hand through the axis of rotation a 1 of the pump aggregation 1, is penetrated perpendicularly by the longitudinal axis of the pressure port 5.
  • a second arrangement plane E1 is selected which is offset parallel to the first arrangement plane E by the vertical eccentricity e.
  • the first connection opening 9a is positioned with respect to the discharge nozzle 5 such that the second arrangement plane E1, which passes through a radial direction vector, on the one hand by the center of the first connection opening 9a and on the other hand by an axial axis of symmetry a 2 of the housing shell 20.1, is penetrated perpendicularly by the longitudinal axis of the pressure port 5. It is understood that the first connection opening 9a can also be arranged between the first and the second arrangement plane E, E1 or in a narrow sectoral area, viewed in the circumferential direction of the centrifugal pump 2, next to these arrangement planes E, E1, without departing from the invention becomes.
  • the return line 9 communicates via a second connection opening 9b with the inner space 20.3, the second connection opening 9b being able to be arranged on the housing jacket 20.1 or on the housing cover 20.2 or on the suction nozzle 20.2a or on a suction line 24.
  • the return line 9 between the two connection openings 9 a, 9 b is preferably divided and the ends are connected to one another with a screw 26.
  • a shut-off valve 22 is arranged in this, which is remotely controllable in a preferred embodiment.
  • the remotely controllable shut-off valve 22 is connected via a control line 27 to a signal transmitter 23 which is arranged, for example, in the discharge nozzle 5 or in a pressure line 25 and generates a control signal from a physical variable characterizing the liquid conveyance in the pump aggregation 1 ( Figures 2 . 3 ).
  • a preferred embodiment of the housing 2.1 / 2.2 and the annular channel 3 *, 3 ** of the centrifugal pump 2 show the Figures 2 and 4 to 7 .
  • the front housing part 2.1 ( FIGS. 6 . 2 ) has an outer peripheral wall 29 of the annular channel 3 *, 3 ** forming, circular, substantially cylindrically extending outer annular channel housing wall 2.1a and the latter emerging from the discharge nozzle 5, which is connected tangentially to the outer annular channel housing wall 2.1a is.
  • the rear housing part 2.2 has the inner circumferential wall 30 of the annular channel 3 *, 3 ** forming inner annular channel housing wall 2.2a, which preferably runs parallel to the outer annular channel housing wall 2.1a.
  • the annular channel 3 *, 3 ** is preferably formed in an axially adjacent region of the impeller plane, which, seen in the flow direction, is behind the impeller 4 and exclusively completely outside the region covered by the impeller 4.
  • the lateral boundary surface 2.2b is part of the rear housing part 2.2); it is preferably radially aligned and bounds the annular channel 3 *, 3 ** in the axial direction as the rear, frontal wall region.
  • the features of the invention characterizing and advantageously ausgestaltenden features are exemplified in the above-defined preferred embodiment of the housing 2.1 / 2.2 and the annular channel 3 *, 3 ** represented ( FIGS. 4 to 7 ) and explained in their mode of action.
  • the ring channel 3 *, 3 ** has in the illustrated meridian plane ( FIG. 6 ) a local ring channel width s, the center of which is defined by a respective half local ring channel width s / 2 shown.
  • a longitudinal axis a 3 of the first connection opening 9a is a radial offset ⁇ r eccentrically offset to the lateral extent of the lateral boundary surface 2.2b and radially offset inwardly, the latter being within the annular channel 3 *, 3 ** as the end wall 31.
  • the bulge according to the invention leads to a reduction in the number of flow vortices and, on the other hand, to a reduction in their intensity in the return line 9.
  • This reduced turbulence particularly in a tube region of the return line 9 directly adjoining the inlet region to the first connection opening 9a, has an in FIG. 7 B2, the flow losses and the Homogenmaschines bin (mixing, distribution and distribution of Gas mecanicengept into the liquid) in the return line 9, which further reduces the suction time of the pump aggregation 1 and the supply of the positive displacement pump 20 with less gas laden Fluid further improved becomes.
  • the second flow region B2 is noticeably slimmer and less narrowing in cross-section than without these features.
  • first connection opening 9a is widened towards the annular channel 3 *, 3 ** initially in the form of a countersink 32 ( FIG. 6 ).
  • the bulge 33 engages in the axial direction either only in the countersink 32 or through it completely into the first connection opening 9a or the inner diameter of the return line 9 therethrough. If the bulge 33 engages axially only in the countersink 32, then only the countersink 32 widens toward the annular channel 3 *, 3 **. If it passes through the countersink 32, then, as seen in the direction of flow through the return line 9, the first connection opening 9a or the inner diameter of the return line 9 widens toward the annular channel 3 *, 3 **.
  • the countersink 32 can be completely or even partially covered in the radial direction by the bulge 33.
  • This countersink 32 may be conical, conical or conical or tulip-shaped, wherein the transition to the inner tube of the return line 9 is preferably rounded, ie preferably convexly curved, designed to avoid or at least reduce a constriction of the pipe flow.
  • a preferably cutting shaping of the countersink 32 is simplified if the latter is formed axially symmetrical and coaxial to the longitudinal axis a 3 .
  • the annular channel-side end portion of the inner tube of the return line can serve, for example, as a guide for the cutting shaping tool.
  • a further improvement of the inflow conditions to and the inlet conditions in the first port opening 9a and thus in the return line 9 adjusts ( FIG. 6 ),
  • the longitudinal axis a 3 of the first connection opening 9a is arranged eccentrically offset from the radial extension region of the lateral boundary surface 2.2b and radially inwardly.
  • the radial offset of the longitudinal axis a 3 enhances the formation of the recirculation flow R and also ensures its sustainable generation.
  • the invention provides two alternative variants.
  • the first variant is characterized in that the longitudinal axis a 3 is perpendicular to and at the point of contact of the tangent to the lateral boundary surface 2.2b.
  • the longitudinal axis a 3 viewed in the direction of flow of the return line 9, is oriented radially inwards toward the center of the pump aggregation 1.
  • the choice of the two variants mentioned is also dependent on the course of the lateral boundary surface 2.2b.
  • the centrifugal pump technique knows annular channels with circular, oval, elliptical, trapezoidal radially outwardly expanding, rectangular or square passage cross-section.
  • the result is whether the flow can enter the first connection opening 9a to the return line 9 more or less smoothly. Bump-free entry can be brought about by changing the angle of inclination between the longitudinal axis a 3 and the direction of the lateral boundary surface 2.2b.
  • the degree of deflection of the entering into the return line 9 flow in the region of the first connection opening 9a can be reduced.
  • the first connection opening 9a is located, for example, in the middle region of the first quadrant of the circular cross section of the annular channel 3 *, 3 **, then the first variant (longitudinal axis a 3 is perpendicular to and at the point of contact of the tangent to the lateral boundary surface 2.2b) are applied, because then the longitudinal axis a 3 , seen in the direction of flow of the return line 9, is already aligned per se radially inward.
  • annular channel 3 *, 3 ** provides a radially oriented lateral boundary surface 2.2b
  • a further improvement of the inflow conditions for and the inlet conditions into the first connection opening 9a results from a proposal which provides that an axis of symmetry a 4 of FIG Bump 33 forms an angle w with the perpendicular to the lateral boundary surface 2.2b longitudinal axis a 3 , wherein the axial extension direction of the bulge 33 is oriented radially inwardly.
  • the above embodiment can be aerodynamically further optimized in that a low point of the bulge 33, viewed in the direction of the center of the pump aggregation 1, recedes radially inwards behind the inner peripheral wall 30 and that the bulge 33 with the transition surface 34 in steadily the inner peripheral wall 30 passes.
  • the embodiments of the pump aggregation 1 described above include the bulge 33 and / or the countersink 32 and / or the radial offset of the first connection opening 9a in accordance with the claims. Any meaningful combination of these inventive features, starting in each case from the realization of the bulge 33, is executable and each provides a solution that has advantages over the acknowledged relevant prior art.
  • the bulge 33 can directly follow the first connection opening 9a, the latter being offset radially or centered in the annular channel 3 *, 3 ** can be arranged.
  • the annular channel 3 *, 3 ** itself can be realized in relation to the area covered by the impeller 4 in the most different axial positions, which are applied in the claims and also indicated in the above description.
  • the annular channel 3 *, 3 ** is designed either as a vane-free annular space 3 * with a passage cross section which is constant over the circumference or as a spiral annular channel 3 ** with a continuously changing passage cross section.
  • the cross-sectional shape of the annular channel 3 *, 3 ** may be circular, oval, elliptical, trapezoidal and radially outwardly enlarging, rectangular or square.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Sustainable Development (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Claims (12)

  1. Unité de pompage auto-amorçante (1), représentant un raccordement en série d'une pompe à anneau liquide fonctionnant comme une pompe volumétrique (20) rotative et d'une pompe centrifuge (2) à amorçage normal,
    - dans laquelle la pompe centrifuge (2) présente un arbre (8) monté de façon rotative avec une roue (4) dans un boîtier (2.1/2.2) doté d'une ouverture d'admission (2.1b) et d'une tubulure de refoulement (5),
    - dans laquelle le boîtier (2.1/2.2), vu dans la direction d'écoulement, est constitué d'une partie de boîtier avant (2.1) et d'une partie de boîtier arrière (2.2) et forme un canal annulaire (3* ; 3**), lequel entoure la région de la roue (4) radialement sur le côté extérieur, soit dans le plan de la roue et/ou dans au moins une région axialement adjacente,
    - dans laquelle l'ouverture d'admission (2.1b) est disposée coaxialement sur la partie de boîtier avant (2.1),
    - dans laquelle un espace intérieur (20.3) délimité par une enveloppe de boîtier (20.1) de la pompe volumétrique (20) est relié à un espace intérieur côté aspiration (2.1c) de la pompe centrifuge (2) par le biais de l'ouverture d'admission (2.1b) et une vis transporteuse (21) fixée sur l'arbre (8) pénétrant à travers la roue (4) et dans l'enveloppe de boîtier (20.1) est disposée dans l'enveloppe de boîtier (20.1),
    - dans laquelle il est prévu une conduite de retour (9) transportant des liquides, laquelle relie le canal annulaire (3* ; 3**) à l'espace intérieur (20.3),
    - dans laquelle la conduite de retour (9) débouche côté canal annulaire par le biais d'une première ouverture de raccordement (9a), laquelle est disposée sur une surface de délimitation latérale (2.2b) du canal annulaire (3* ; 3**) s'étendant latéralement par rapport au plan de la roue, caractérisée en ce que
    - la première ouverture de raccordement (9a) possède un renflement (33) entourant sectoriellement un axe longitudinal (a3) de la première ouverture de raccordement (9a),
    - en ce que le renflement (33) est orienté unilatéralement et vers le centre de l'unité de pompage (1),
    - en ce que le renflement (33) élargit continuellement la première ouverture de raccordement (9a) vers le canal annulaire (3* ; 3**), de façon directe ou indirecte,
    - et en ce que le renflement (33) se prolonge continuellement dans la surface de délimitation latérale (2.2b) ou dans une paroi périphérique intérieure (30) du canal annulaire (3* ; 3**) se raccordant à celle-ci, avec une surface de transition (34) au niveau de sa section d'extrémité tournée vers le canal annulaire (3* ; 3**).
  2. Unité de pompage auto-amorçante (1) selon la revendication 1,
    caractérisée en ce que
    - la partie de boîtier avant (2.1) présente la paroi de boîtier de canal annulaire extérieure (2.1a) circulaire, s'étendant essentiellement cylindriquement, formant une paroi périphérique extérieure (29) du canal annulaire (3* ; 3**), ainsi que la tubulure de refoulement (5) débouchant de celle-ci, laquelle est raccordée tangentiellement à la paroi de boîtier de canal annulaire extérieure (2.1a),
    - en ce que la partie de boîtier arrière (2.2) présente la paroi de boîtier de canal annulaire intérieure (2.2a) formant la paroi périphérique intérieure (30) du canal annulaire (3* ; 3**), et s'étendant parallèlement à la paroi de boîtier de canal annulaire extérieure (2.1a),
    - en ce que le canal annulaire (3* ; 3**) est formé dans une région axialement adjacente au plan de la roue, laquelle, vu dans la direction d'écoulement, se trouve en aval de la roue (4) et exclusivement à l'extérieur de la région occupée par la roue (4),
    - et en ce que la surface de délimitation latérale (2.2b) fait partie de la partie de boîtier arrière (2.2), tout en étant orientée radialement et en bordant le canal annulaire (3* ; 3**) dans la direction axiale, en tant que région de paroi tout à l'arrière du côté frontal.
  3. Unité de pompage auto-amorçante selon la revendication 1 ou 2,
    caractérisée en ce que
    - la première ouverture de raccordement (9a) s'élargit vers le canal annulaire (3* ; 3**) tout d'abord sous la forme d'une cavité (32),
    - et en ce que le renflement (33) traverse la cavité (32) ou s'introduit dans celle-ci dans la direction axiale, tout en élargissant ainsi continuellement la cavité (32) vers le canal annulaire (3* ; 3**).
  4. Unité de pompage auto-amorçante selon la revendication 3,
    caractérisée en ce que
    - la cavité (32) est formée de façon axialement symétrique et coaxialement à l'axe longitudinal (a3).
  5. Unité de pompage auto-amorçante selon l'une des revendications précédentes,
    caractérisée en ce que
    - l'axe longitudinal (a3) est disposé de façon excentrée par rapport à la région d'extension radiale de la surface de délimitation latérale (2.2b), tout en étant radialement décalé vers l'intérieur.
  6. Unité de pompage auto-amorçante selon la revendication 5,
    caractérisée en ce que
    - l'axe longitudinal (a3) est espacé de la paroi périphérique intérieure (30) délimitant radialement le canal annulaire (3* ; 3**) du côté intérieur, à l'exception d'un demi-diamètre intérieur de la conduite de retour (9).
  7. Unité de pompage auto-amorçante selon l'une des revendications précédentes,
    caractérisée en ce que
    - l'axe longitudinal (a3) s'étend perpendiculairement à la tangente et au niveau du point de contact entre celle-ci et la surface de délimitation latérale (2.2b).
  8. Unité de pompage auto-amorçante (1) selon la revendication 7, comprenant une surface de délimitation latérale (2.2b) orientée radialement,
    caractérisée en ce que
    - un axe de symétrie (a4) du renflement (33) forme un angle (w) avec l'axe longitudinal (a3) s'étendant perpendiculairement à la surface de délimitation latérale (2.2b), la direction d'extension axiale du renflement (33) étant orientée radialement vers l'intérieur.
  9. Unité de pompage auto-amorçante (1) selon la revendication 8,
    caractérisée en ce que
    - un point de fond du renflement (33), vu dans la direction vers le centre de l'unité de pompage (1), est en retrait radialement vers l'intérieur derrière la paroi périphérique intérieure (30),
    - et en ce que le renflement (33) se prolonge continuellement dans la paroi périphérique intérieure (30) avec la surface de transition (34).
  10. Unité de pompage auto-amorçante selon l'une des revendications 1 à 6,
    caractérisée en ce que
    - l'axe longitudinal (3a), vu dans la direction d'écoulement à travers la conduite de retour (9), est orienté radialement vers l'intérieur vers le centre de l'unité de pompage (1).
  11. Unité de pompage auto-amorçante selon l'une des revendications précédentes,
    caractérisée en ce que
    - la première ouverture de raccordement (9a) est positionnée de telle façon par rapport à la tubulure de refoulement (5), qu'un premier plan d'agencement (E) passant à travers un vecteur directionnel radial, lequel s'étend d'une part à travers le point central de la première ouverture de raccordement (9a) et d'autre part à travers un axe de rotation (a1) de l'unité de pompage (1), est traversé perpendiculairement par l'axe longitudinal de la tubulure de refoulement (5).
  12. Unité de pompage auto-amorçante selon l'une des revendications précédentes 1 à 10,
    caractérisée en ce que
    - la première ouverture de raccordement (9a) est positionnée de telle façon par rapport à la tubulure de refoulement (5), qu'un deuxième plan d'agencement (E1) passant à travers un vecteur directionnel radial, lequel s'étend d'une part à travers le point central de la première ouverture de raccordement (9a) et d'autre part à travers un axe de symétrie axial (a2) de l'enveloppe de boîtier (20.1), est traversé perpendiculairement par l'axe longitudinal de la tubulure de refoulement (5).
EP16726880.4A 2015-06-08 2016-06-03 Ensemble de pompes à amorçage automatique Active EP3303845B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PL16726880T PL3303845T3 (pl) 2015-06-08 2016-06-03 Samozasysający agregat pompowy

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102015007100.9A DE102015007100A1 (de) 2015-06-08 2015-06-08 Selbstansaugende Pumpenaggregation
PCT/EP2016/062665 WO2016198334A1 (fr) 2015-06-08 2016-06-03 Ensemble de pompes à amorçage automatique

Publications (2)

Publication Number Publication Date
EP3303845A1 EP3303845A1 (fr) 2018-04-11
EP3303845B1 true EP3303845B1 (fr) 2019-07-31

Family

ID=56098260

Family Applications (1)

Application Number Title Priority Date Filing Date
EP16726880.4A Active EP3303845B1 (fr) 2015-06-08 2016-06-03 Ensemble de pompes à amorçage automatique

Country Status (7)

Country Link
US (1) US10634145B2 (fr)
EP (1) EP3303845B1 (fr)
CN (1) CN107820544B (fr)
DE (1) DE102015007100A1 (fr)
ES (1) ES2748809T3 (fr)
PL (1) PL3303845T3 (fr)
WO (1) WO2016198334A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE202020100267U1 (de) * 2020-01-20 2021-04-22 Evoguard Gmbh Selbstansaugende Pumpe und Vorrichtung

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR3096093B1 (fr) * 2019-05-14 2023-02-24 Ams R&D Sas Dispositif pour l’aspiration de liquide se trouvant sur un sol.
CN111523186B (zh) * 2020-05-19 2024-01-19 重庆水泵厂有限责任公司 双吸水泵用吸水室形状的优化方法

Family Cites Families (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AT158125B (de) * 1938-05-12 1940-03-11 Armaturen U Maschinenfabrik Ag Kreiselpumpe mit einer Wasserringpumpe als Entlüftungspumpe, der über einen Umschalthahn Schmierwasser zugeführt wird.
GB1292194A (en) 1970-04-10 1972-10-11 Stuart Turner Ltd Self-priming centrifugal pump
JPH01203696A (ja) * 1988-02-08 1989-08-16 Matsushita Electric Ind Co Ltd 自動呼び水式遠心ポンプ
DE3929758C2 (de) * 1989-09-07 1994-11-17 Klein Schanzlin & Becker Ag Kreiselpumpengehäuse in Blechbauweise
ITVI980028A1 (it) 1998-02-13 1999-08-13 Calpeda A Spa Pompa autodescante ad eiettore con dispositivo di controllo del flusso
DK200000278U4 (da) 2000-09-20 2002-01-11 Apv Fluid Handling Horsens As Hygiejnisk selvansugende centrifugalpumpe.
DE20305113U1 (de) 2002-06-22 2003-06-26 Tuchenhagen Gmbh Leitvorrichtung für ein in Blechbauweise ausgeführtes Gehäuse einer Kreiselpumpe
US6779974B2 (en) * 2002-12-11 2004-08-24 Polyvane Technology Corp. Device of a volute channel of a pump
JP4284270B2 (ja) * 2004-12-07 2009-06-24 長野ポンプ株式会社 消防用ポンプ
DE102007032228B4 (de) 2007-07-11 2016-01-07 Gea Tuchenhagen Gmbh Selbstansaugende Pumpenaggregation
CN202209282U (zh) * 2011-08-31 2012-05-02 重庆市星格水泵有限公司 高抗汽蚀快速自吸泵
CN202545268U (zh) * 2012-03-06 2012-11-21 东莞市众隆电机电器制造有限公司 自吸性压力液泵

Non-Patent Citations (1)

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

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE202020100267U1 (de) * 2020-01-20 2021-04-22 Evoguard Gmbh Selbstansaugende Pumpe und Vorrichtung

Also Published As

Publication number Publication date
EP3303845A1 (fr) 2018-04-11
CN107820544B (zh) 2019-09-10
PL3303845T3 (pl) 2020-02-28
DE102015007100A1 (de) 2016-12-08
WO2016198334A1 (fr) 2016-12-15
US10634145B2 (en) 2020-04-28
CN107820544A (zh) 2018-03-20
US20180340523A1 (en) 2018-11-29
ES2748809T3 (es) 2020-03-18

Similar Documents

Publication Publication Date Title
DE102010046870B4 (de) Seitenkanalgebläse, insbesondere Sekundärluftgebläse für eine Verbrennungskraftmaschine
EP2171279B1 (fr) Ensemble de pompes à amorçage automatique
DE1817430A1 (de) Regenerativkompressor
EP2382393B1 (fr) Soufflante de canal latéral, en particulier soufflante d'air secondaire pour une machine à combustion interne
EP0934466A1 (fr) Pompe d'alimentation
EP3303845B1 (fr) Ensemble de pompes à amorçage automatique
DE112015002306T5 (de) Turbolader
DE102015100215B4 (de) Seitenkanalgebläse für eine Verbrennungskraftmaschine
EP2104787B1 (fr) Soufflante radiale et nettoyeur à haute pression pourvu d'une soufflante radiale
EP2207979B1 (fr) Machine hydrodynamique, notamment retardateur hydrodynamique
WO2016176712A1 (fr) Pompe à liquide de refroidissement pour moteur à combustion interne
DE2163011B2 (de) Seitenkanalarbeitsmaschine
EP2342464B1 (fr) Ventilateur à canal latéral, en particulier turbine secondaire pour un moteur à combustion interne
EP3464904B1 (fr) Pompe centrifuge pour produits alimentaires liquides sensibles à la chaleur et rotor pour une pompe centrifuge de ce type
EP2582983B1 (fr) Pompe centrifuge double flux
DE202007019540U1 (de) Selbstansaugende Pumpenaggregation
EP3728860B1 (fr) Compresseurs à canal latéral, en particulier compresseurs d'air secondaires pour un moteur à combustion interne
DE102014118210B4 (de) Mehrflutige Strömungsmaschine
EP2342465A1 (fr) Soufflante à canal latéral, en particulier turbine secondaire pour un moteur à combustion interne
DE19706004C2 (de) Gebläse-Einrichtung zum Befördern von Fluiden in Rohrleitungen
EP3805521A1 (fr) Pompe à palettes
DE1528804B2 (de) Axialkreiselpumpe
EP2587065A1 (fr) Compresseur à anneau liquide
DE1528864A1 (de) Umdrehungsmaschine
EP1375924A2 (fr) Volute de pompe centrifuge

Legal Events

Date Code Title Description
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: 20171211

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: 20190122

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: CH

Ref legal event code: EP

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REG Reference to a national code

Ref country code: AT

Ref legal event code: REF

Ref document number: 1161186

Country of ref document: AT

Kind code of ref document: T

Effective date: 20190815

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: DE

Ref legal event code: R096

Ref document number: 502016005811

Country of ref document: DE

REG Reference to a national code

Ref country code: SE

Ref legal event code: TRGR

REG Reference to a national code

Ref country code: NL

Ref legal event code: MP

Effective date: 20190731

REG Reference to a national code

Ref country code: LT

Ref legal event code: MG4D

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

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: 20191202

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: 20190731

Ref country code: NL

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: 20190731

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: 20190731

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: 20190731

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: 20191031

Ref country code: NO

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: 20191031

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

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: 20190731

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: 20191101

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: 20190731

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: 20191130

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: 20190731

REG Reference to a national code

Ref country code: ES

Ref legal event code: FG2A

Ref document number: 2748809

Country of ref document: ES

Kind code of ref document: T3

Effective date: 20200318

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: 20190731

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

Ref country code: IT

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: 20190731

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: 20190731

Ref country code: DK

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: 20190731

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: 20190731

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

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: 20190731

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: 20190731

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: 20200224

Ref country code: CZ

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: 20190731

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 502016005811

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

PG2D Information on lapse in contracting state deleted

Ref country code: IS

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: 20191030

26N No opposition filed

Effective date: 20200603

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

Ref country code: SI

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: 20190731

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: 20190731

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20200603

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

Ref country code: LU

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

Effective date: 20200603

REG Reference to a national code

Ref country code: BE

Ref legal event code: MM

Effective date: 20200630

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: 20200603

Ref country code: GB

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

Effective date: 20200603

Ref country code: CH

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

Effective date: 20200630

Ref country code: LI

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

Effective date: 20200630

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: 20200630

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: 20190731

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: 20190731

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: 20190731

REG Reference to a national code

Ref country code: AT

Ref legal event code: MM01

Ref document number: 1161186

Country of ref document: AT

Kind code of ref document: T

Effective date: 20210603

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

Ref country code: AT

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

Effective date: 20210603

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

Effective date: 20230601

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

Ref country code: FR

Payment date: 20230622

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: 20230622

Year of fee payment: 8

Ref country code: PL

Payment date: 20230602

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: 20230719

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: 20230810

Year of fee payment: 8