EP3805570A1 - Pompe centrifuge permettant de transporter un fluide - Google Patents

Pompe centrifuge permettant de transporter un fluide Download PDF

Info

Publication number
EP3805570A1
EP3805570A1 EP20195762.8A EP20195762A EP3805570A1 EP 3805570 A1 EP3805570 A1 EP 3805570A1 EP 20195762 A EP20195762 A EP 20195762A EP 3805570 A1 EP3805570 A1 EP 3805570A1
Authority
EP
European Patent Office
Prior art keywords
wear ring
impeller
centrifugal pump
pump according
axial direction
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Withdrawn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
EP20195762.8A
Other languages
German (de)
English (en)
Inventor
Thomas Welschinger
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.)
Sulzer Management AG
Original Assignee
Sulzer Management AG
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 Sulzer Management AG filed Critical Sulzer Management AG
Publication of EP3805570A1 publication Critical patent/EP3805570A1/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Withdrawn legal-status Critical Current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
    • F04D29/08—Sealings
    • F04D29/16—Sealings between pressure and suction sides
    • F04D29/165—Sealings between pressure and suction sides especially adapted for liquid pumps
    • F04D29/167—Sealings between pressure and suction sides especially adapted for liquid pumps of a centrifugal flow wheel
    • 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

Definitions

  • the invention relates to a centrifugal pump for conveying a fluid according to the preamble of the independent claim.
  • Centrifugal pumps which are designed, for example, as centrifugal pumps with a radial impeller, are used in many different technological areas, for example in the oil and gas processing industry, in the water industry or in the context of industrial energy generation. Many different embodiments are known here, for example single-stage pumps, multi-stage pumps, single-flow pumps or double-flow pumps.
  • the centrifugal pump comprises a suction chamber which is flow-connected to the inlet of the pump, and a pressure chamber which is flow-connected to the outlet of the pump.
  • An impeller which is arranged non-rotatably on a shaft, conveys the fluid, for example water, from the suction chamber into the pressure chamber and thereby increases the pressure of the fluid.
  • each stage has a suction space and a pressure space, the pressure space of one stage representing the suction space of the next stage, so to speak.
  • the impeller is designed, for example, as a closed impeller.
  • the impeller comprises a hub disk on which a plurality of blades are arranged, and a cover disk which completely or at least partially covers the blades on their side facing away from the hub disk.
  • a cover disk which completely or at least partially covers the blades on their side facing away from the hub disk.
  • the shaft on which the impeller is arranged is set in rotation by a drive, for example an electric motor, and rotates around the axis of the shaft, which defines an axial direction.
  • a drive for example an electric motor
  • the impeller is arranged in a stationary housing part of the pump housing.
  • a non-rotating wear ring, which surrounds the impeller, is usually provided between the impeller, which rotates in the operating state, and the stationary housing part.
  • the wear ring is arranged, for example, in such a way that it surrounds a central area of the cover disk of the impeller. This creates a radial sealing gap which separates the pressure chamber from the suction chamber.
  • the area between the front side of the impeller, for example the cover plate, and the stationary housing part is also referred to as the side space of the pump.
  • part of the pumped fluid flows from the pressure chamber through the side chamber and the radial sealing gap back into the suction chamber of the pump.
  • the wear ring is designed with a predetermined clearance with respect to the rotating impeller, so that the annular radial sealing gap is formed between a radially inner, cylinder jacket-shaped boundary surface of the wear ring and the rotating impeller, through which a leakage flow from the pressure chamber to the suction chamber is made possible.
  • This arrangement is often referred to as a labyrinth.
  • the leakage flow is advantageous on the one hand because it contributes to the hydrodynamic stabilization of the rotor (shaft with impeller), on the other hand it also means a certain loss in terms of the efficiency of the pump.
  • the dimensioning of this radial sealing gap therefore plays an important role. The aim is to avoid direct physical contact between the stationary wear ring and the rotating shaft during operation of the pump.
  • the radial sealing gap must not be made too narrow, because radial movements of the impeller can occur during operation of the pump, for example due to the bending of the Wave.
  • the width of the radial sealing gap by which its extent in the radial direction is meant, can also change in the course of operation, for example due to erosion on the wear ring.
  • the dimensions of the radial sealing gap therefore always represent a compromise between the efficiency of the pump and the operational reliability of the pump.
  • a centrifugal pump for conveying a fluid with a suction chamber, a pressure chamber and an impeller arranged rotatably about an axial direction, with which the fluid can be pumped from the suction chamber into the pressure chamber, and with a wear ring that cannot rotate on a stationary housing part is arranged, wherein the wear ring delimits a radial sealing gap together with the impeller, wherein the wear ring is arranged displaceably in the axial direction, wherein a preload element is provided which exerts a force on the wear ring which is directed in the axial direction towards the impeller is, and wherein the wear ring is designed and arranged such that, in the operating state, a hydraulic force also acts on the wear ring, which is directed in the axial direction towards the impeller.
  • the wear ring is thus mounted in a floating manner with respect to the axial direction and is pressed onto the impeller in the axial direction by the prestressing element.
  • the fluid to be conveyed penetrates from the pressure chamber through the radial sealing gap and thereby lifts the wear ring off the impeller in the axial direction against the force of the pretensioning element.
  • the wear ring is designed and arranged in such a way that the fluid also exerts a hydraulic force on the wear ring, this hydraulic force being directed in the axial direction towards the impeller. This additional hydraulic force thus acts on the wear ring in the same direction as the force exerted on the wear ring by the pretensioning element.
  • the axial sealing gap is formed between the impeller and the wear ring, which forms a lubricating film between the wear ring and the impeller. Further opening of the axial sealing gap is prevented by the joint action of the hydraulic force, which tries to press the wear ring onto the impeller, and the force exerted on the wear ring by the pretensioning element.
  • the function of the radial sealing gap between the impeller and the wear ring which is known from the prior art, is mainly performed by the axial sealing gap in the configuration according to the invention.
  • the radial sealing gap can therefore be made even larger than in the prior art, that is to say with a larger width. This has the great advantage that, in the operating state, physical contact between the impeller and the wear ring in the area of the radial sealing gap can be prevented more reliably.
  • the wear ring and the pretensioning element are preferably designed such that, in the operating state, there is an axial sealing gap between the impeller and the wear ring which is smaller than the radial sealing gap.
  • the prestressing element is preferably designed as a spring element, for example in the form of compression springs, cup springs or corrugated springs
  • a rotation lock is provided which prevents the wear ring from rotating.
  • the wear ring can be displaced in the axial direction, it cannot rotate about the axial direction.
  • the wear ring has a front end face facing the impeller and a pressure surface facing away from the impeller, the pressure surface and the stationary housing part delimiting a rear space into which the fluid can penetrate from the pressure space.
  • a radial gap is provided between a radially outer surface of the wear ring and the stationary housing part through which the fluid can penetrate from the pressure chamber into the rear chamber.
  • a sealing element is preferably provided between the wear ring and the stationary housing part, which sealing element is designed and arranged in such a way that it seals off the rear space from the suction space.
  • This sealing element which is designed as an O-ring, for example, makes it particularly easy to ensure that the fluid can only get back into the suction chamber via the axial sealing gap.
  • the prestressing element acts on the pressure surface of the wear ring.
  • the wear ring is designed with a Z-shaped profile.
  • the wear ring has a rear end face which is different from the pressure surface, the rear end face being parallel to the pressure surface and being arranged at a distance from the pressure surface with respect to the axial direction.
  • the prestressing element acts on the rear end face.
  • Another preferred measure consists in that the sealing element is arranged between the rear end face and the pressure face with respect to the axial direction.
  • the impeller is particularly preferably designed as a closed impeller, that is to say, the impeller has a cover plate which interacts with the wear ring.
  • a race can be provided on the impeller or on the cover disk, which is connected to the impeller in a rotationally fixed manner and which interacts with the wear ring.
  • the centrifugal pump is designed as a centrifugal pump in which the impeller is designed as a radial impeller.
  • centrifugal pump which is designed as a single-stage, single-flow centrifugal pump. It goes without saying that the invention is not restricted to such centrifugal pumps, but rather relates to centrifugal pumps in general.
  • the centrifugal pump according to the invention can also be designed as a multi-stage pump or as a double-flow pump.
  • Fig. 1 shows, in a sectional view, an exemplary embodiment of a centrifugal pump according to the invention for conveying a fluid, which is designated in its entirety by the reference symbol 1.
  • a centrifugal pump 1 which is designed as a centrifugal pump 1 with a covered impeller 2, the impeller 2 being designed as a radial impeller 2.
  • Covered running wheels 2 are also referred to as closed running wheels 2.
  • the impeller 2 has a hub disk 21 which is non-rotatably connected to a shaft 3, several blades 22, which are arranged on the hub disk 21, and a cover disk 23, which the blades 22 on their side or edge facing away from the hub disk 21 at least partially covered. This creates several channels in the impeller 2 through which the fluid is conveyed.
  • the centrifugal pump 1 also has a suction chamber 4, which is flow-connected to an inlet 41 for the fluid, and a pressure chamber 5, which is connected to the an outlet 51 for the fluid is in flow communication.
  • the impeller 2 is arranged in a housing part 6 and is surrounded by the housing part 6.
  • the shaft 3 is driven to rotate about its longitudinal or central axis, which defines an axial direction A, by a drive (not shown), for example an electric motor.
  • a drive for example an electric motor.
  • the shaft 3 rotates together with the impeller 2 arranged on it in the axial direction A. This rotation sucks the fluid out of the suction chamber 4 and delivers it from the impeller 2 into the pressure chamber 5, from where the fluid goes to the outlet 51 of the pump 1 can stream.
  • the direction of the longitudinal axis of the shaft 3 is always meant.
  • the radial direction then means a direction perpendicular to the axial direction A.
  • part of the delivered fluid flows back from the pressure chamber 5 through a side chamber 7 of the centrifugal pump into the suction chamber 4 of the centrifugal pump 1.
  • the side space 7 is that space which is delimited in the axial direction A on the one hand by the stationary housing part 6 and on the other hand by the cover plate 23 of the impeller 2 a non-rotatably arranged wear ring 8 is provided on the stationary housing part 6, which wear ring cooperates with the impeller 2, more precisely with the cover plate 23 of the impeller 2.
  • Fig. 2 shows in an enlarged detail the impeller 2, the stationary housing part 6 and the wear ring 8 of an embodiment of the centrifugal pump 1 according to the invention.
  • the wear ring 8 has an L-shaped profile, with one leg of the L-shaped profile - here the longer leg -
  • the cover plate 23 surrounds radially on the outside.
  • the other leg of the L-shaped profile forms an axial front end face 81 which faces the impeller 2 and rests on the end face of the cover disk 23.
  • the wear ring 8 is arranged in an annular groove 9 which is provided in the stationary housing part 6 and which surrounds the shaft 3 coaxially.
  • the wear ring 8 is secured against rotation or rotation about the axial direction A in the groove 9 by a rotation lock 10.
  • the rotation lock 10 is designed, for example, as a pin which engages on the one hand in the stationary housing part 6 and on the other hand in a bore in the wear ring 8. With respect to the axial direction A, the wear ring 8 is arranged displaceably.
  • the longer leg of the wear ring 8 is designed in such a way that a radial sealing gap 11 is formed between this leg and the cover plate 23 of the impeller 2. This means that the radially inner surface of the leg of the wear ring 8 and the radially outer surface of the cover disk 23 of the impeller 2 delimit the radial sealing gap 11.
  • Such an arrangement in which a sealing gap is provided between a suction space and a pressure space or more generally between two spaces in which different pressures prevail in the operating state, which is limited on the one hand by a rotating part and on the other hand by a stationary part of the pump, is often also known as a labyrinth.
  • a prestressing element 12 which exerts a force on the wear ring 8 which is directed in the axial direction A towards the impeller 2.
  • the prestressing element 12 is preferably designed as a spring element.
  • the prestressing element 12 can comprise one or more springs, each spring being designed, for example, as a compression spring, a plate spring or a corrugated spring.
  • the wear ring 8 also has an axial pressure surface 82 which faces away from the impeller 2.
  • the pressure surface 82 is arranged in the groove 9 of the stationary housing part 6, so that the pressure surface 82 and the stationary housing part 6 - namely the bottom of the groove 9 - delimit a rear space 14.
  • the prestressing element 12 is arranged in this rear space 14, which is supported on the one hand on the stationary housing part 6 and on the other hand on the pressure surface 82 of the wear ring 8, so that the wear ring 8 is prestressed by the prestressing element 12 against the cover plate 23 of the impeller 2.
  • the wear ring 8 is designed in such a way that a radial gap 15 is provided between a radially outer surface 83 of the wear ring 8 and the stationary housing part 6, through which the fluid can pass from the pressure chamber 5 into the rear chamber 14.
  • the delivered fluid can flow from the pressure chamber 5 through the radial gap 15 into the rear chamber 14 and build up a pressure there.
  • a sealing element 16 is provided between the wear ring 8 and the stationary housing part 6, which sealing element 16 is arranged in such a way that it seals off the rear space 14 from the suction space 4.
  • the pressure drop from the pressure in the rear space 14 to the suction pressure in the suction space 4 takes place via this sealing element 16.
  • the sealing element 16 is preferably designed as an O-ring.
  • the sealing element 16 is arranged on the radially inner wall of the groove 9.
  • this wall of the groove 9 can have an annular recess into which the sealing element 16 is inserted. It is also possible that an annular recess is provided in the wear ring 8, into which the sealing element 16 is inserted. be.
  • the pressurized fluid can penetrate from the pressure chamber 5 through the radial gap 15 into the rear chamber 14, but cannot flow out of the rear chamber 14 into the suction chamber 4 due to the sealing element 16. In the operating state, therefore, a pressure builds up in the rear space 14 which, in addition to the prestressing element 12, exerts a hydraulic force on the wear ring 8, which tries to push it in the axial direction A in the direction of the impeller 2.
  • the pressurized fluid from the pressure chamber 5 passes through the radial sealing gap 11 to the front end face 81 of the wear ring 8.
  • the pressure of the fluid also acts on the wear ring 8 in the operating state, which forces the wear ring 8 in the axial direction A from the impeller 2, more precisely the cover plate 23 tries to push away.
  • three forces act on the wear ring the hydraulic force generated by the pretensioning element 12 and the pressure in the rear chamber 14 act in the direction of the impeller 2 on the wear ring 8, and furthermore, the one under pressure Fluid generates a force which tries to push the wear ring 8 away from the impeller 2.
  • an axial sealing gap 17 opens between the front end face 81 of the wear ring 8 and the impeller 2, more precisely the cover plate 23, which allows a leakage flow from the pressure chamber 5 through the radial sealing gap 11 and the axial sealing gap 17 in the suction chamber 4 allows.
  • the radial sealing gap 11 between the wear ring 8 and the impeller 2 can be made wider than is possible in the prior art.
  • the width of the radial sealing gap 11 means its extension in the radial direction.
  • a wider radial sealing gap 11 has the advantage that physical contact between the impeller 2 and the wear ring 8 can be avoided even when the impeller 1 moves in the radial direction, as can be caused, for example, by bending of the shaft 3.
  • the axial sealing gap 17 between the impeller 2 and the wear ring 8 preferably has a smaller width than the radial sealing gap 11.
  • the centrifugal pump 1 works as follows. When the centrifugal pump 1 is at a standstill, the front end face 81 of the wear ring rests against the cover disk 23 of the impeller 2. When the centrifugal pump is put into operation and the impeller 2 rotates, a fluid film builds up in the axial sealing gap 17, which is delimited by the floating wear ring 8, which keeps the axial sealing gap 17 open. At the same time, the now additionally acting pressure in the rear space 14 ensures that the axial sealing gap 17 does not open too far. A dynamic equilibrium is therefore established, which enables a small leakage flow from the pressure chamber 5 into the suction chamber 4.
  • a race 24 on the impeller 2 is shown in Fig. 3 first variant shown. Apart from the race 24, this first variant is configured the same as that in FIG Fig. 2 illustrated embodiment.
  • the race 24 is in a correspondingly shaped recess arranged in the cover disk 23 of the impeller 2 in such a way that its radially outer boundary surface is opposite the radially inner boundary surface of the wear ring 8.
  • the wear ring 8 and the race 24 are arranged coaxially and together delimit the radial sealing gap 11, which is arranged between the wear ring 8 and the race 24.
  • the race 24 is designed in such a way that it extends inwards at least as far in the radial direction as the axial end face 81 of the wear ring 8.
  • the race 24 extends somewhat further inwards in the radial direction than Axial end face 81 of the wear ring 8.
  • the race 24 extends in the axial direction A in the direction of view of the impeller 2 at least as far as the longer leg of the L-shaped profile of the wear ring 8
  • the race 24 preferably protrudes beyond the longer leg of the wear ring 8, as seen in the direction of the blades 22 of the impeller 2 with respect to the axial direction A.
  • This configuration ensures that the wear ring 8 can only come into contact with the race 24 of the impeller, but not with other components of the cover plate 23 or the impeller 2.
  • compensating bores 25 are provided in the impeller 2, more precisely in the hub disk 21, each of which extends completely through the hub disk 21 in the axial direction A. These compensating bores 25 reduce the axial thrust acting on the impeller 2 and thus relieve the axial bearing of the centrifugal pump 1. The compensating bores 25 relieve the pressure on the side of the hub disk 21 facing away from the cover disk 23 in the area of the shaft 3.
  • the radially outer region of the hub disk 21 delimits a rear side space 71, which adjoins the pressure space 5 in a similar manner to the side space 7
  • a further labyrinth 10 is provided on the radially inner area of the hub disk 21, which creates a radial annular gap between the hub disk 21, which rotates in the operating state, and that of the hub disk 21 opposite stationary part includes.
  • this labyrinth 10 can also be designed in the same way with a wear ring floating in the axial direction A, as has been explained with reference to the wear ring 8.
  • the labyrinth 10 can also comprise a raceway in the same way as was explained with reference to the raceway 24.
  • the wear ring 8 has an essentially Z-shaped profile, with an annular radially outer part 86, an annular radially inner part 87 and a middle part 85, which connects the radially outer part 86 to the radially inner part 87.
  • the pressure surface 82 which delimits the rear space 14, is formed by the middle part 85.
  • the wear ring 8 also has a rear end face 84 which delimits the radially inner part 87 in the axial direction A.
  • the rear end face 84 is therefore different from the pressure surface 82, the rear end face 84 and the pressure surface 82 being parallel to one another and spaced apart from one another with respect to the axial direction A.
  • the prestressing element 12 is arranged such that it acts on the rear end face 84, that is, the prestressing element 12 is supported on the one hand on the stationary housing part 6 and on the other hand on the rear end face 84 of the wear ring 8.
  • the third variant shown corresponds to that in Fig 4 shown second variant, except that in the third variant in the same way as in the first variant ( Fig. 3 ) the race 24 is provided on the cover plate 23 of the impeller 2.
  • the fourth variant shown is very similar to the second variant ( Fig. 4 ), but in the fourth variant the prestressing element 12 is arranged in the rear space 14 so that the prestressing element 12 acts on the pressure surface 82 of the wear ring 8.
  • the prestressing element 12 is supported on the one hand on the stationary housing part 6 and on the other hand on the pressure surface 82 of the wear ring 8.
  • the sealing element 16 is also arranged in the fourth variant with respect to the axial direction A between the pressure surface 82 and the rear end surface 84, so that the sealing element 16 seals the rear space 14 from the suction space 4.
  • the invention is not limited to one-step or single-flow inventions.
  • the centrifugal pump according to the invention can in particular be designed as a double-flow pump. It goes without saying that both labyrinths, namely that between the first suction space and the pressure space and that between the second suction space and the pressure space, can then be designed according to the invention.
  • the invention is suitable for every labyrinth in a centrifugal pump, the labyrinth being an arrangement in which two rooms, in which different pressures prevail in the operating state, are connected to one another via a sealing gap between a rotating part of the centrifugal pump and a relative the pump housing is arranged stationary part.
  • each labyrinth in a centrifugal pump can be designed according to the invention.
  • the labyrinth between two adjacent stages can in particular also be designed according to the invention.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
EP20195762.8A 2019-10-09 2020-09-11 Pompe centrifuge permettant de transporter un fluide Withdrawn EP3805570A1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP19202303 2019-10-09

Publications (1)

Publication Number Publication Date
EP3805570A1 true EP3805570A1 (fr) 2021-04-14

Family

ID=68242509

Family Applications (1)

Application Number Title Priority Date Filing Date
EP20195762.8A Withdrawn EP3805570A1 (fr) 2019-10-09 2020-09-11 Pompe centrifuge permettant de transporter un fluide

Country Status (1)

Country Link
EP (1) EP3805570A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20210164484A1 (en) * 2019-12-02 2021-06-03 Sulzer Management Ag Pump with a lifting device
CN113309732A (zh) * 2021-05-31 2021-08-27 景德镇学院 一种气体输送装置
CN115059622A (zh) * 2022-06-27 2022-09-16 南京科技职业学院 一种含有防砂功能的潜水排污泵

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1116886A1 (fr) * 2000-01-11 2001-07-18 Sulzer Pumpen Ag Machine rotative pour fluide à jeu d'étanchéité radial entre les parties du stator et un rotor
EP1808603A1 (fr) * 2006-01-12 2007-07-18 Sulzer Pumpen Ag Machine rotative pour fluide à jeu d'étanchéité radial
CN205805998U (zh) * 2016-07-01 2016-12-14 南京林业大学 一种无内漏轴向力自平衡的离心式流体输送装置
WO2017158003A1 (fr) * 2016-03-16 2017-09-21 Ksb Aktiengesellschaft Pompe centrifuge avec un ensemble pour la réduction d'un reflux

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1116886A1 (fr) * 2000-01-11 2001-07-18 Sulzer Pumpen Ag Machine rotative pour fluide à jeu d'étanchéité radial entre les parties du stator et un rotor
EP1808603A1 (fr) * 2006-01-12 2007-07-18 Sulzer Pumpen Ag Machine rotative pour fluide à jeu d'étanchéité radial
WO2017158003A1 (fr) * 2016-03-16 2017-09-21 Ksb Aktiengesellschaft Pompe centrifuge avec un ensemble pour la réduction d'un reflux
CN205805998U (zh) * 2016-07-01 2016-12-14 南京林业大学 一种无内漏轴向力自平衡的离心式流体输送装置

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20210164484A1 (en) * 2019-12-02 2021-06-03 Sulzer Management Ag Pump with a lifting device
CN113309732A (zh) * 2021-05-31 2021-08-27 景德镇学院 一种气体输送装置
CN115059622A (zh) * 2022-06-27 2022-09-16 南京科技职业学院 一种含有防砂功能的潜水排污泵

Similar Documents

Publication Publication Date Title
EP3805570A1 (fr) Pompe centrifuge permettant de transporter un fluide
EP2406497B1 (fr) Machine hydraulique à engrenage
DE4212169C2 (de) Dynamisches Sperrsystem für das Schmieröl der Lager eines Zentrifugalkompressors
DE2939945A1 (de) Schneckenmaschine mit axial nachgiebiger dichtung
DE2315747A1 (de) Mechanische dichtung mit verbesserter leckverluststeuerung
DE19519799B4 (de) Kreiselpumpe
WO2015074903A1 (fr) Dispositif de décharge
DE2825616C2 (de) Lager- und Dichtungsanordnung an den Wellen einer Zahnradpumpe
DE102009037443B4 (de) Selbstansaugende Flügelzellenpumpe
EP3199815B1 (fr) Pompe centrifuge
DE2146695B2 (de) Wellenabdichtung für den Elektromotor eines Tauchpumpenaggregates
EP1777417A1 (fr) Turbocompresseur
EP2707629B1 (fr) Dispositif d'étanchéification d'une chambre de pompage d'une pompe à piston tournant, et pompe à piston tournant dotée de ce dispositif
DE3925404C2 (fr)
DE112006000321T5 (de) Dichtungsstruktur einer Turbomolekularpumpe
DE2539425B1 (de) Axialschubgleitlager fuer zentrifugalpumpen und ventilatoren
EP4291810A1 (fr) Agencement de compresseur à consommation réduite de gaz de traitement
DE102009038937A1 (de) Anordnung in einem Schraubenverdichter
EP2216550B1 (fr) Pompe à engrenages à joint d'étanchéité d'arbre
EP2286088B1 (fr) Pompe
EP2119869A2 (fr) Hydromachine
EP3140550B1 (fr) Dispositif d'étanchéité pour une pompe haute pression et pompe haute pression dotée d'un tel dispositif d'étanchéité
DE102020133327B4 (de) Pumpenanordnung
DE2632523A1 (de) Kreiselpumpe
EP2153075A1 (fr) Palier

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

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

Free format text: STATUS: THE APPLICATION HAS BEEN PUBLISHED

AK Designated contracting states

Kind code of ref document: A1

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

AX Request for extension of the european patent

Extension state: BA ME

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

Free format text: STATUS: REQUEST FOR EXAMINATION WAS MADE

17P Request for examination filed

Effective date: 20211014

RBV Designated contracting states (corrected)

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

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: 20230401