EP1953390A1 - Dispositif et procédé d'égalisation de poussée axiale - Google Patents

Dispositif et procédé d'égalisation de poussée axiale Download PDF

Info

Publication number
EP1953390A1
EP1953390A1 EP07002435A EP07002435A EP1953390A1 EP 1953390 A1 EP1953390 A1 EP 1953390A1 EP 07002435 A EP07002435 A EP 07002435A EP 07002435 A EP07002435 A EP 07002435A EP 1953390 A1 EP1953390 A1 EP 1953390A1
Authority
EP
European Patent Office
Prior art keywords
pump
pressure
shaft
piston
unit
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.)
Withdrawn
Application number
EP07002435A
Other languages
German (de)
English (en)
Inventor
Johann Neiszer
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.)
Ritz Pumpenfabrik GmbH and Co KG
Original Assignee
Ritz Pumpenfabrik GmbH and Co KG
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 Ritz Pumpenfabrik GmbH and Co KG filed Critical Ritz Pumpenfabrik GmbH and Co KG
Priority to EP07002435A priority Critical patent/EP1953390A1/fr
Priority to US12/025,844 priority patent/US20080187434A1/en
Publication of EP1953390A1 publication Critical patent/EP1953390A1/fr
Withdrawn legal-status Critical Current

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
    • F04D29/00—Details, component parts, or accessories
    • F04D29/04—Shafts or bearings, or assemblies thereof
    • F04D29/041—Axial thrust balancing
    • F04D29/0416—Axial thrust balancing balancing pistons

Definitions

  • the invention relates to a pump, in particular a vertical pump, according to claim 1, a method for compensating the axial thrust in a pump according to claim 18, and a method for retrofitting an axial thrust compensation to a pump according to claim 19 and a retrofit module according to claim 22.
  • the pumps considered here have at least one impeller which is driven by a shaft of at least one drive unit, wherein in operation acts on the shaft of the impeller corresponding to the pump pressure axial thrust.
  • a vertical pump is understood here to mean a pump in which the pump shaft is aligned substantially vertically in use.
  • DD 231829 is a method for Axialschubaus protest described in centrifugal pumps, in which also a compensating piston is provided at which a pressure difference is generated by the pump pressure and a supplied via a discharge water return line lower pressure.
  • a speed measuring device and pressure measuring points which are arranged in front of and behind the balance piston, pass the measured data to a computer, which determines the resulting axial thrust according to the speed.
  • a valve mounted in the relief water return passage is controlled so as to set a relief pressure at which the difference disappears.
  • Another object of the invention is to provide a method for retrofitting an axial thrust balance on an existing pump, in particular vertical pump, so that even existing pumps can use the axial thrust compensation invention or the inventive method for Axialschubaus protest is used.
  • another object of the invention is to provide a retrofit module for a self-regulated axial thrust balance on a pump.
  • the pump according to the invention has at least one centrifugal pump unit with at least one impeller which can be driven by at least one drive unit, wherein an axial thrust arising during operation of the pump acts on the shaft of the impeller. Furthermore, a self-adjusting the axial thrust at least partially supporting compensating piston is provided, which is non-positively connected in the axial direction of the shaft with the shaft.
  • the essence of the invention is to provide a compensation device for acting on the shaft of the pump in operation axial thrust, a force-locking in the axial direction of the shaft connected to the shaft and guided in a compensating cylinder compensating piston for generating a self-regulating dependent on the axial thrust of the pump and this provided on the shaft of the drive unit opposite acting compensation force.
  • the self-regulating compensation force is generated from a differential pressure between the pump pressure occurring during operation of the pump and any lower pressure than the pump pressure.
  • a compensating piston which at least partially supports the axial thrust is connected in a non-positive manner to the shaft in the axial direction of the shaft.
  • the balance piston can be mounted substantially anywhere on the shaft. When mounted between the pump unit and the drive unit, a very compact construction, in particular with a vertical pump, becomes possible. In addition, this allows a particularly favorable supply of the respective pressure to the corresponding piston side.
  • the function of the balance piston is self-regulating, which can be dispensed with in comparison to solutions in the prior art to additional measuring and control devices. This leads to a significant reduction in manufacturing and cost.
  • the thus less loaded thrust bearing can be made smaller and made simpler, which also leads to a reduction in manufacturing costs and minimizes costs. Furthermore, the service life and operational safety of the thrust bearings increase.
  • the arrangement of balancing piston and compensating cylinder, in particular the effective piston surface is tuned to the rated power of the drive unit.
  • the size of the piston surface on the production side can be chosen so that at maximum pump power or rated power, the relief force generated is so large that the resulting axial thrust is at most compensated. If the vote is made in relation to the maximum power, also a reversal of the axial thrust is reliably prevented, for example, in a large-sized piston surface.
  • the cylinder is fastened to the side of the engine facing the pump.
  • the compact design is additionally supported. Furthermore, so construction, installation and maintenance effort is minimized because, for example, a mounting plane to the drive unit already exists and in contrast to the pump side does not have to be generated first.
  • the arrangement of compensating piston and compensating cylinder is provided in the conveying direction in front of the centrifugal pump unit.
  • balance piston and balance cylinder can act as a hydraulic additional bearing, which contributes to a considerable relief of the axial bearing, which in turn can be significantly smaller and simpler structure.
  • the additional hydraulic bearing runs almost wear-free and has a much lower frictional resistance than conventional thrust bearings.
  • the suction pressure of the centrifugal pump unit as the lower pressure because a direct fluidic connection from the suction side of the centrifugal pump unit to the corresponding side of the balance piston, namely the piston side facing the centrifugal pump unit, can be made very easily.
  • the ambient pressure, or any other predetermined lower pressure than the pump pressure via a corresponding compensation line can be supplied.
  • the ambient pressure is used as the lower pressure, a retrofitting of the device according to the invention on conventional vertical pumps without structural changes to the pump is possible.
  • the side of the compensating piston, at which the higher pressure is to rest is in direct fluid communication with the pressure side of the pump. In such a constructive simple design of the pump pressure acts directly and lossless on the balance piston.
  • the lower pressure In order to be able to counteract the axial thrust, the lower pressure must be supplied to the side of the compensating piston, which points in the direction of the resulting unloading force. In a structurally simple embodiment, this is done via a compensation line that can be easily adapted to the circumstances of existing drive and / or pump units.
  • the compensation line is provided as an axial bore in the shaft of the drive unit and / or the centrifugal pump unit in an advantageous development of the invention.
  • the drive unit is arranged above the centrifugal pump unit.
  • the ambient pressure can be guided over an axial bore as a compensation line in the current through the drive unit shaft to the corresponding side of the balance piston in an advantageous manner.
  • the suction pressure can be passed through a corresponding axial bore as a compensation line through the current through the centrifugal pump unit shaft to the corresponding side of the balance piston.
  • the vertical pump may have a single shaft as drive and pump shaft, but embodiments with an articulated shaft arrangement are also possible, in particular if the individual functional units are of modular design and thus the pump is scalable.
  • the drive unit can also be located below the centrifugal pump unit, then change the above statements accordingly.
  • the Ausreteskolben- / cylinder assembly is designed as a retrofit module.
  • a retrofit module may for example be equipped with corresponding flanges that it can be easily attached between the drive unit and the pump unit at the flanges.
  • a stationary cylinder is then integrated, in which a piston is movably provided, which can be suitably fixedly connected to the shaft of the pump impeller or the drive unit.
  • the retrofit module can be mounted as a piston / cylinder set in an existing or to be created space between the drive unit and the pump unit directly on the shaft of the pump impeller or the drive unit.
  • the cylinder can for example be attached to the housing of the drive unit, so that the piston is slidably held therein.
  • the above-described supply of the predetermined low pressure via equalization line which is realized as a bore in a shaft of the vertical pump, is suitable, as doing the retrofitting such a pressure line or equalization line essentially consists in the exchange of the shaft and structural interventions in the pump housing accounts for the most part.
  • the required holes in the shaft can be particularly easily realized in modular vertical pumps, where the application-related pump dimensioning on the number of installed centrifugal pump modules or drive modules (scaling) takes place.
  • the required shaft holes due to their relatively short length dimension can be produced technically simple.
  • Fig. 1 shows an embodiment of a vertical pump according to the invention.
  • the vertical pump in the simplest case is understood as meaning the combination of a drive unit with a centrifugal pump unit which are arranged substantially vertically one above the other.
  • a vertical pump here refers to a pump in which the pump shaft is aligned substantially vertically in use.
  • "down" in the vertical pump is defined by the suction side of the pump unit, and "vertical" in the vertical pump corresponds to the pressure side of the pump unit.
  • the vertical pump of Fig. 1 consists of a drive unit 1, which may be, for example, an electric motor and a centrifugal pump unit 2, which is fixed by means of a flange on the drive unit 1.
  • a drive shaft or shaft 4 of the drive unit 1 is aligned vertically. It protrudes with its lower end out of the housing of the drive unit 1.
  • an impeller 5 of the centrifugal pump unit 2 is fixed and secured, for example by means of a tongue and groove connection 6 against rotation and by a nut 7 at the shaft end against slipping off or sliding down.
  • Around the impeller 5 around a pump housing 8 is arranged, which is flanged with its upper end to the drive unit 1 by means of a flange connection 3.
  • the lower end forms the suction port 9 of the pump second
  • a piston / cylinder arrangement for axial thrust compensation. It consists of a compensating piston 10 which is rotatably and axially not slidably mounted on the shaft 4, and a cylinder 14. Both exist preferably made of corrosion-resistant steel (eg stainless steel, duplex, NiResist or cast bronze).
  • the cylinder 14 is fixedly connected to the underside of the drive unit 1 and aligned coaxially with the shaft 4 of the drive unit 1. It separates the top and bottom 11, 12 of the piston 10 substantially fluid-tight, but not mandatory fluid-tight, against each other. It has been found that a gap dimension in the sense of fluid-tight is sufficient, in which the influence of frictional forces in the piston-cylinder arrangement according to the invention is reduced.
  • a discharge space 15 In the unloaded state, accordingly Fig. 1
  • the bottom 10 of the piston 10 is in direct fluid communication with the high pressure side of the centrifugal pump unit 2.
  • flange 3 Above the flange 3 are compensating lines 18 from the outside horizontally through the Housing the drive unit 1 out, which open into the discharge chamber 15. About this compensation lines 18 is fed through not shown further channels or differently shaped lines of the piston top 11 a selected or predetermined low pressure, which may be, for example, the suction pressure or the ambient pressure. It is noted that “lower pressure” here means any predetermined pressure that is lower than the pump pressure currently in operation of the pump.
  • the compensation lines 18 for supplying a selected or predetermined lower pressure can be avoided if, as mentioned above, an axial bore, not shown in the figures is provided by the shaft 4 of the drive unit 1, which opens into the discharge chamber 15.
  • the axial bore accordingly Fig. 1 be guided from above into the region of the balance piston 10 when the ambient pressure is to be supplied as a predetermined low pressure. Accordingly, the axial through hole is guided from below into the region of the balance piston 10 when the suction pressure is to be supplied as a predetermined low pressure.
  • Fig. 2 schematically shows another embodiment of the piston / cylinder arrangement for Axialschubaus protest.
  • the operating principle is basically the same as in the arrangement of Fig. 1 ,
  • the balance piston 10 is again arranged. It is guided in the cylinder 14, which separates the piston bottom 12 from the top 11 substantially fluid-tight, for example, as described above by a small gap.
  • the relief chamber 15 enclosed by cylinder 14 and piston 10 is connected to the high-pressure side of the centrifugal pump unit 2, which thus acts on the piston underside 12.
  • the upper side 11 is subjected to a lower pressure.
  • the arrangement of Fig. 2 additionally forms a hydrostatic additional bearing, the advantages of which will be described below.
  • Fig. 3 shows a further embodiment of the device according to the invention.
  • the piston / cylinder arrangement according to the invention is arranged above the vertical pump above the housing of the drive unit 1.
  • the shaft 4 of the drive unit 1 is extended so far that it projects beyond the upper end of the drive unit.
  • At this end of the balance piston 10 is attached. He is from the cylinder 14 laterally and additionally enclosed above and below.
  • 10 chambers 15, 16 are formed on both sides of the piston.
  • the cylinder is attached to the housing of the drive unit 1, so that the piston 10 is guided therein displaceable vertically.
  • the overlying the piston 10 chamber 15 is connected via a compensation line with the environment in connection, that is, in the chamber 15 there is ambient pressure, the chamber 16 located underneath it is supplied with the pump pressure.
  • the pump pressure from above means an axial bore in the shaft 4 of the drive unit 1 of the chamber 16 supply.
  • a fluid to be delivered for example groundwater or mine water
  • a fluid to be delivered is conveyed through the suction opening 9 essentially in the axial direction upward through the centrifugal pump unit 2, ie in the conveying direction, in which it is guided past the drive unit by means of corresponding channels 20 in the housing.
  • the axial thrust generated by the delivery thrust and directed counter to it acts on the impeller 5 and presses it over the pump shaft 4 counter to the conveying direction of the pump 2 downwards.
  • the resulting from the pressure difference at a constant piston area on the piston 10 relief force depends on the pump pressure and the selected lower Pressure off.
  • the unloading force acting against the axial thrust increases.
  • a self-adjusting adaptation of the axial thrust relief to the axial thrust takes place.
  • the axial thrust decreases. Due to the sinking delivery pressure but also the pressure difference at the balance piston 10, which also reduces the resulting discharge force drops. Even when the delivery pressure decreases, an adjustment of the unloading force to the axial thrust takes place in a self-regulating manner.
  • the relief force is proportional to the piston surface at a constant pressure difference, this can be designed so that in the region of the maximum axial thrust, a desired reduction of the maximum axial thrust is at maximum pumping pressure, ie at maximum delivery pressure Force acting on the thrust bearing is such that the thrust bearing always runs in the area for which it was specified.
  • a force reversal by the unloading force is avoided, which would additionally burden the normally much weaker designed axial counter bearing.
  • FIG. 2 An embodiment of the piston / cylinder arrangement for Axialschubaus Panda accordingly Fig. 2 forms as already mentioned an additional hydrostatic bearing.
  • discharge chamber 15 there is delivery pressure.
  • a balance between the axial thrust and the unloading force adjusts itself in accordance with the pressure difference prevailing on the compensating piston 10 and the size of the piston surface.
  • This arrangement thus forms a hydraulic bearing. That is, the balance piston is not supported against a second tread, but on a fluid cushion, which is formed by the delivery pressure in the cylinder 14.
  • the bearing runs almost wear-free and has a much lower frictional resistance.
  • a passage of the shaft 4 through the bottom of the cylinder 14, as in Fig. 2 shown is not necessary in this embodiment.
  • the pump pressure must be supplied to the discharge chamber 15 via a compensation line, not shown.
  • the invention is not limited to the embodiments of FIGS. 1 to 3 limited.
  • the pump and drive unit have separate shafts, it is possible to accommodate the balance piston / cylinder assembly only in the pump or only in the drive unit.
  • the device according to the invention with two pistons, wherein the pistons are each acted upon on one side by the higher or lower pressure and the corresponding other sides of the pistons communicate with one another, so that the pressure difference can additionally be influenced in the case of different piston surfaces.
  • a compensation of the axial thrust in a pump, in particular a vertical pump, with at least one drive unit and at least one centrifugal pump unit is proposed.
  • in operation of the pump acts on a balance piston which is axially non-displaceably connected to the shaft of the impeller of the centrifugal pump unit, resulting from the pump pressure and a lower pressure pressure difference from the axial thrust directed opposite and on the shaft of the impeller attacking force is generated.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Control Of Non-Positive-Displacement Pumps (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
EP07002435A 2007-02-05 2007-02-05 Dispositif et procédé d'égalisation de poussée axiale Withdrawn EP1953390A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP07002435A EP1953390A1 (fr) 2007-02-05 2007-02-05 Dispositif et procédé d'égalisation de poussée axiale
US12/025,844 US20080187434A1 (en) 2007-02-05 2008-02-05 Device and procedure for axial thrust compensation

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP07002435A EP1953390A1 (fr) 2007-02-05 2007-02-05 Dispositif et procédé d'égalisation de poussée axiale

Publications (1)

Publication Number Publication Date
EP1953390A1 true EP1953390A1 (fr) 2008-08-06

Family

ID=38222283

Family Applications (1)

Application Number Title Priority Date Filing Date
EP07002435A Withdrawn EP1953390A1 (fr) 2007-02-05 2007-02-05 Dispositif et procédé d'égalisation de poussée axiale

Country Status (2)

Country Link
US (1) US20080187434A1 (fr)
EP (1) EP1953390A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110985551A (zh) * 2019-11-08 2020-04-10 西安泵阀总厂有限公司 一种长距离立式浮动支撑轴系结构
CN112814918A (zh) * 2020-12-30 2021-05-18 东方电气集团东方汽轮机有限公司 一种立式汽轮给水泵同轴一体转子结构

Families Citing this family (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
IT1393311B1 (it) * 2009-03-19 2012-04-20 Turboden Srl Turbina per espansione di gas/vapore con mezzi di contrasto della spinta assiale sull'albero di uscita
EP2565419A1 (fr) * 2011-08-30 2013-03-06 Siemens Aktiengesellschaft Refroidissement d'une turbomachine
US11326607B2 (en) 2019-02-05 2022-05-10 Saudi Arabian Oil Company Balancing axial thrust in submersible well pumps
US10844701B2 (en) 2019-02-05 2020-11-24 Saudi Arabian Oil Company Balancing axial thrust in submersible well pumps
US11371326B2 (en) 2020-06-01 2022-06-28 Saudi Arabian Oil Company Downhole pump with switched reluctance motor
US11499563B2 (en) 2020-08-24 2022-11-15 Saudi Arabian Oil Company Self-balancing thrust disk
US11920469B2 (en) 2020-09-08 2024-03-05 Saudi Arabian Oil Company Determining fluid parameters
US11644351B2 (en) 2021-03-19 2023-05-09 Saudi Arabian Oil Company Multiphase flow and salinity meter with dual opposite handed helical resonators
US11591899B2 (en) 2021-04-05 2023-02-28 Saudi Arabian Oil Company Wellbore density meter using a rotor and diffuser
US11913464B2 (en) 2021-04-15 2024-02-27 Saudi Arabian Oil Company Lubricating an electric submersible pump
US11994016B2 (en) 2021-12-09 2024-05-28 Saudi Arabian Oil Company Downhole phase separation in deviated wells
US12012550B2 (en) 2021-12-13 2024-06-18 Saudi Arabian Oil Company Attenuated acid formulations for acid stimulation

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE280678C (fr) * 1906-05-21
DE178665C (fr) *
FR1133318A (fr) * 1955-01-04 1957-03-26 Rateau Soc équilibre axial des mobiles de turbo-machines convenant en particulier aux turbomachines à axe vertical ou incliné
DE1528717A1 (de) * 1965-06-30 1969-10-30 Halbergerhuette Gmbh Vorrichtung zum Ausgleich des Axialschubes bei mehrstufigen Kreiselpumpen
NL7712699A (en) * 1977-11-17 1979-05-21 Stork Koninklijke Maschf Centrifugal pump with thrust load counteraction - has component on shaft between high and low-pressure chambers

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3225698A (en) * 1963-11-29 1965-12-28 Buffalo Forge Co Hermetic motor-pump construction
US4234293A (en) * 1979-03-27 1980-11-18 Dresser Industries, Inc. Axial balancing system for motor driven pumps
US4472107A (en) * 1982-08-03 1984-09-18 Union Carbide Corporation Rotary fluid handling machine having reduced fluid leakage
US6309174B1 (en) * 1997-02-28 2001-10-30 Fluid Equipment Development Company, Llc Thrust bearing for multistage centrifugal pumps

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE178665C (fr) *
DE280678C (fr) * 1906-05-21
FR1133318A (fr) * 1955-01-04 1957-03-26 Rateau Soc équilibre axial des mobiles de turbo-machines convenant en particulier aux turbomachines à axe vertical ou incliné
DE1528717A1 (de) * 1965-06-30 1969-10-30 Halbergerhuette Gmbh Vorrichtung zum Ausgleich des Axialschubes bei mehrstufigen Kreiselpumpen
NL7712699A (en) * 1977-11-17 1979-05-21 Stork Koninklijke Maschf Centrifugal pump with thrust load counteraction - has component on shaft between high and low-pressure chambers

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110985551A (zh) * 2019-11-08 2020-04-10 西安泵阀总厂有限公司 一种长距离立式浮动支撑轴系结构
CN110985551B (zh) * 2019-11-08 2021-08-06 西安泵阀总厂有限公司 一种长距离立式浮动支撑轴系结构
CN112814918A (zh) * 2020-12-30 2021-05-18 东方电气集团东方汽轮机有限公司 一种立式汽轮给水泵同轴一体转子结构

Also Published As

Publication number Publication date
US20080187434A1 (en) 2008-08-07

Similar Documents

Publication Publication Date Title
EP1953390A1 (fr) Dispositif et procédé d'égalisation de poussée axiale
EP2307726B1 (fr) Pompe à cylindrée variable
EP3491253A1 (fr) Système d'entraînement électro-hydrostatique
DE102006035378A1 (de) Fahrzeugbremsvorrichtung
EP3003807B1 (fr) Releveur de frein électrohydraulique et ensemble de freinage
EP1985853B1 (fr) Pompe à piston radial, en particulier pour systèmes d'injection Common Rail (CR)
EP1461533B1 (fr) Pompe
DE2208172B2 (de) Vorrichtung zur Dampfung des belastungsbedingten Druckanstiegs bei hydrostatischen Antneben
DE3313390A1 (de) Oelpumpenanordnung
DE1924417A1 (de) Hubsteuerung fuer hydraulische Pumpen
EP1654136A1 (fr) Systeme d'entrainement hydrostatique avec separation de masse de liquide hydraulique cote pompe, pour deux circuits hydrauliques
DE102020109134A1 (de) Axialkolbenmaschine
EP3003808B1 (fr) Unité fonctionnelle et releveur de frein électrohydraulique équipé d'une telle unité
DE19654781A1 (de) Hilfseinrichtung zur Realisierung einer Redundanz für die Energieversorgung von Flugsteuerungsantrieben
DE4208925C1 (fr)
DE102007022022A1 (de) Hydrostatische Maschine und diese verwendender Wandler
DE60104096T2 (de) Rückführeinrichtung für lecköl eines hydraulikmotors
DE102007051185A1 (de) Hydrostatischer Antrieb
EP0749380B1 (fr) Systeme de freinage hydraulique a regulation antipatinage et antiblocage
EP2441967A1 (fr) Dispositif de commande pour consommateurs hydrauliques
WO2022156949A1 (fr) Pompe à broches à vis
DE102005043252B4 (de) Verdrängerpumpe mit variablem Fördervolumen
DE19855899A1 (de) Axialkolbenmaschine
DE4342487B4 (de) Hydrostatisches Antriebssystem mit Nachsaugeventil
DE102014202411A1 (de) Elektrisch angesteuertes Druckregelventil für eine verstellbare hydrostatische Pumpe und eine verstellbare hydrostatische Pumpe mit einem Druckregelventil

Legal Events

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

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU LV MC NL PL PT RO SE SI SK TR

AX Request for extension of the european patent

Extension state: AL BA HR MK RS

AKX Designation fees paid
STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE APPLICATION IS DEEMED TO BE WITHDRAWN

18D Application deemed to be withdrawn

Effective date: 20090207

REG Reference to a national code

Ref country code: DE

Ref legal event code: 8566