WO2024022850A1 - Pompe centrifuge avec joint d'étanchéité rotatif pour l'étanchéification de l'espace de roue et procédé de fabrication d'une roue de pompe - Google Patents

Pompe centrifuge avec joint d'étanchéité rotatif pour l'étanchéification de l'espace de roue et procédé de fabrication d'une roue de pompe Download PDF

Info

Publication number
WO2024022850A1
WO2024022850A1 PCT/EP2023/069695 EP2023069695W WO2024022850A1 WO 2024022850 A1 WO2024022850 A1 WO 2024022850A1 EP 2023069695 W EP2023069695 W EP 2023069695W WO 2024022850 A1 WO2024022850 A1 WO 2024022850A1
Authority
WO
WIPO (PCT)
Prior art keywords
impeller
bearing ring
pump
centrifugal pump
rotating
Prior art date
Application number
PCT/EP2023/069695
Other languages
German (de)
English (en)
Inventor
David KRILL
Patrick Hauck
Original Assignee
KSB SE & Co. KGaA
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 KSB SE & Co. KGaA filed Critical KSB SE & Co. KGaA
Publication of WO2024022850A1 publication Critical patent/WO2024022850A1/fr

Links

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
    • F04D29/02—Selection of particular materials
    • F04D29/026—Selection of particular materials 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
    • F04D29/04—Shafts or bearings, or assemblies thereof
    • F04D29/041—Axial thrust balancing
    • 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
    • F04D29/0413—Axial thrust balancing hydrostatic; hydrodynamic thrust bearings
    • 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
    • F04D29/18—Rotors
    • F04D29/22—Rotors specially for centrifugal pumps
    • F04D29/2205—Conventional flow pattern
    • F04D29/2222—Construction and assembly
    • 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
    • F04D29/18—Rotors
    • F04D29/22—Rotors specially for centrifugal pumps
    • F04D29/2261—Rotors specially for centrifugal pumps with special measures
    • F04D29/2266—Rotors specially for centrifugal pumps with special measures for sealing or thrust balance
    • 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
    • F05D2250/51—Inlet

Definitions

  • the invention relates to a centrifugal pump with at least one pump impeller and with at least one mechanical seal arranged between the pump impeller under the pump housing for sealing the impeller gap between the suction and pressure sides of the centrifugal pump, as well as a method for producing a pump impeller for such a centrifugal pump.
  • centrifugal pumps Due to their design, centrifugal pumps have a gap between the impeller and the housing.
  • there is a need to provide sufficient space between the impeller and the housing in order to avoid a certain axial offset without threatening damage due to deflection of the shaft or the impeller but on the other hand, there is a desire to dimension the gap as small as possible in order to avoid the damage caused by it to minimize the hydraulic losses caused.
  • the latter arise from the backflow of the pumped medium from the pressure side of the impeller through the gap to the suction side. What makes matters worse is that the gap width can continuously increase during operation due to material removal.
  • the object of the present invention is to optimize the sealing of the impeller gap in such a way that the hydraulic losses that occur due to the flow from the pressure side to the suction side are minimized.
  • the mechanical seal includes a rotating component that rotates together with the impeller around the pump's axis of rotation.
  • a stationary component of the mechanical seal is arranged in a rotationally fixed manner within the pump housing.
  • the sliding surfaces of the two components ideally run orthogonally to the axial direction or rotation axis of the pump. Due to the pressure difference between the suction and pressure sides, the pump impeller and thus the rotating component of the mechanical seal is moved in the axial direction towards the stationary component, which ensures optimal sealing and the mechanical seal used also acts as an axial bearing for the pump impeller.
  • the axial seal achieved allows the hydraulic losses that occur across the impeller gap with a radial seal to be reduced.
  • the mechanical seal used consists of a stationary and a rotating component. At least the respective sliding surfaces of the components consist of or include ceramic and/or a carbon material, in particular graphite, and/or a carbon composite material, such as silicon carbide. Both sliding surfaces can be made from identical or different types of material.
  • the rotating component of the mechanical seal can be or include a rotating bearing ring which is connected in a rotationally fixed manner to the pump impeller or a component of the pump impeller.
  • the bearing ring can be on an axial Front edge of the pump impeller can be arranged in the area around its suction mouth, ie the bearing runs around the suction mouth of the impeller.
  • the pump impeller can be designed in several parts, with the rotating bearing ring being able to be attached to the cover plate of the impeller.
  • the rotating component in particular the rotating bearing ring, comprises a sliding surface, in particular an annular sliding surface.
  • the sliding surface runs perpendicular to the rotation axis or axial axis of the pump. It is conceivable that the sliding surface is a continuous surface, in particular a continuous annular surface. Since the pump's fluid flows around the mechanical seal during operation, sufficient lubrication of the mechanical seal is ensured.
  • the sliding surface of the rotating component has one or more worm grooves, in the form of a bearing ring in the form of radial grooves. The formation of lubricating grooves improves the formation of a lubricating film between the sliding surfaces of the mechanical seal.
  • the formation of the locating grooves on the rotating component of the mechanical seal can have another technical advantage. If the oscillating grooves are designed as radial grooves on an annular sliding surface of the rotating component, the rotation of the component creates a pumping effect, which creates a delivery flow that is opposite to the pressure-related volume flow through the gap. Ideally, this further reduces the pressure-related volume flow so that a further minimization of hydraulic losses through the gap can be achieved. However, there is no reason why the sliding surface of the stationary component of the mechanical seal should also or alternatively be equipped with lubricating grooves.
  • the bearing ring or the rotating component of the mechanical seal can be attached to the impeller or a corresponding impeller cover disk after its manufacture and secured mechanically. It is also conceivable that the bearing ring or the rotating component is attached during the manufacturing process of the impeller. It is conceivable, for example, that the impeller or at least the component of the impeller that carries the bearing ring can be manufactured from plastic by injection molding. In this case it makes sense to use the rotating component, restrictively inject the rotating bearing ring directly into the impeller during injection molding.
  • the rotating component has at least one undercut, which is at least partially enclosed by the injection molding material of the pump impeller, whereby the rotating component is fixed in the axial direction on the pump impeller.
  • a suitable undercut can be achieved by varying the outer diameter of the rotating component or the bearing ring.
  • a step-like change in diameter on the outer circumference of the bearing ring is particularly advantageous.
  • the area of the bearing ring with the larger outside diameter is mounted close to the impeller, while the area with a reduced outside diameter is formed at the end of the bearing ring remote from the impeller.
  • the stationary component of the mechanical seal is mounted and fixed in a rotationally fixed manner directly or indirectly on the pump housing, in particular in the suction channel of the pump housing.
  • the mounting of the stationary component on the housing wall can be flexible in order to be able to compensate for any deviations from the plane parallelism of the sliding surfaces of the mechanical seal running on one another.
  • a flexible mounting of the stationary component can be carried out using an elastomer, in particular an O-ring, by means of which the component is mounted on a surface of the pump housing.
  • a certain flexibility of the stationary component is therefore achieved in the compression direction of the elastomer. It is conceivable, for example, that a certain axial movement or tilting of the stationary component away from the impeller is possible.
  • the suction channel preferably has a suitable, in particular annular, stop surface on its inner wall, which runs perpendicular to the axis of rotation or axial axis.
  • the stationary component can be flexibly mounted on this stop surface; in particular, the stationary component lies in the axial direction between the stop surface and the impeller.
  • the axial movement of the stationary component in the direction of the impeller can be limited, whereby the stationary component is in a space formed between the housing wall, in particular the aforementioned one Stop surface and seal carrier are secured.
  • the seal carrier is fixed to the housing wall, in particular fixed in a rotationally fixed manner.
  • the seal carrier can be designed annularly, with its inner diameter being dimensioned larger than the outer circumference of the suction mouth of the impeller, so that the latter can be accommodated at least slightly within the bore of the seal carrier.
  • the stationary component and the bearing carrier are designed like a ring, with the stationary bearing ring and the bearing carrier being arranged coaxially.
  • the inner diameter of the bore of the bearing carrier is dimensioned larger than the inner diameter of the bearing ring, whereby the sliding surface of the stationary bearing ring is exposed for contact with the sliding surface of the rotating bearing ring.
  • the stationary component is preferably secured against rotation about the axial axis via a mechanical connection to the seal carrier. It is conceivable that one or more elements of the stationary component that project in the axial direction are formed, which engage in corresponding complementary grooves in the bearing carrier and thus enable a rotation-proof connection.
  • the present invention relates to a method for producing a pump impeller for a centrifugal pump, in particular for a centrifugal pump according to the invention explained above.
  • the method is characterized by the features of claim 12, according to which the pump impeller or at least part of the pump impeller is manufactured by injection molding and the rotating component of the mechanical seal is at least partially encapsulated during injection molding of the pump impeller.
  • the rotating component and/or the stationary component or their sliding surfaces preferably comprise ceramic and/or a carbon material and/or a carbon composite material.
  • the rotating component is designed in particular as a ring-shaped bearing ring.
  • the component is attached in or on the injection mold in such a way that the rotating component is injected around or behind the impeller in the area of the suction mouth of the impeller.
  • a step-like outer diameter increase is preferably provided on its ring circumference, which forms an undercut when the impeller is injection molded, which is back-injected by the injection molding material. As a result, this undercut is enclosed by the impeller material, so that the bearing ring is axially fixed to the suction mouth.
  • the step has one or more grooves extending in the axial direction through the step. These grooves allow the injection molding material to flow through the grooves behind the undercut.
  • the filled grooves in the bearing ring ensure a rotation-proof fixation on the pump impeller.
  • the pump impeller can be manufactured in several parts, for example consisting of a cover disk and a support disk. At least the cover disk is produced by injection molding, with the rotating component of the mechanical seal being injected in the area particularly around the suction mouth of the cover disk.
  • the support disk can preferably also be produced by injection molding. Both parts of the impeller can be made of plastic.
  • the cover and support disk can be connected, in particular welded, preferably by means of ultrasonic welding.
  • the rotating component i.e. the bearing ring
  • the rotating component is only manufactured to its final size using a material-removing process after the pump impeller has been created and injected into the pump impeller. This measure makes it possible to machine the sliding surface of the rotating sealing component as precisely as possible to ensure plane parallelism with the complementary stationary sealing part.
  • FIG. 1 a perspective view of the impeller of a centrifugal pump according to the invention
  • Fig. 2 a top view of the impeller according to Fig. 1,
  • Fig. 3a, 3b Sectional views of the impeller along the section axes AA and BB,
  • Fig. 4 an individual representation of the rotating bearing ring of the mechanical seal
  • Fig. 5 A perspective top view of the housing of the centrifugal pump with the impeller removed
  • Fig. 7 a schematic sketch of the injection molding tool for producing the pump impeller
  • Fig. 8 an alternative version of the rotating bearing ring for the pump impeller.
  • FIG. 1 shows a perspective top view of the pump impeller 1 of a centrifugal pump according to the invention.
  • the pump impeller 1 is designed in several parts and is composed of a cover disk 2 and a support disk 3. At least the cover plate 2 is made of plastic using an injection molding process. Cover disk 2 and support disk 3 are connected using ultrasonic welding.
  • the impeller 1 includes a suction opening 4, which is coaxial with the axis of rotation and is formed by a cylindrical projection 4a of the cover disk 2.
  • the bearing ring 10 of the mechanical seal rotating with the impeller 1 is arranged at the front outer end of the projection 4a.
  • the external annular surface 10a represents the rotating sliding surface of the mechanical seal and is designed as a continuous annular surface in the exemplary embodiment shown in FIG.
  • An alternative embodiment of the bearing ring 10 is shown in the embodiment of FIG. 8, which will be discussed again later.
  • the cover plate 2 of the impeller 1 is made of plastic using an injection molding process.
  • the bearing ring 10 which is made of ceramic and/or a carbon material and/or a carbon composite material, is injected during the injection molding of the cover plate 2, so that it is fixed to the suction mouth 4 in the axial direction of the pump.
  • the axial fixation is achieved by back-injection 11 of the bearing ring 10.
  • the shape of the bearing ring 10 required for this will be shown below using the detailed illustration in FIG.
  • the perspective view of the bearing ring 10 shows the step-like contour of the outer circumference.
  • the inside diameter is constant over the axial length, but the outer circumference includes a portion 12a with a larger outside diameter and a portion 12b with a reduced outside diameter.
  • the partial area 12a with a larger outside diameter rests on the suction mouth 4 of the impeller 1.
  • the step-like diameter reduction forms an undercut 11 of the bearing ring 10, which can be back-injected when the cover disk 2 is injection molded in order to achieve the axial fixation mentioned.
  • the area 12a with a larger outer diameter is also provided with axially extending grooves or recesses 13 which extend completely through the partial area 120a in the axial direction.
  • the injection molding material can flow in particular through the grooves 13 to the area 12b with a reduced diameter, whereby the step 11 is completely enclosed by the material of the cover disk 2.
  • This can be seen in the sectional view along the sectional axis BB of Figure 3, which shows a complete enclosure of the partial area 12a by the material 2a of the cover plate 2.
  • the cutting plane runs in the area of a groove 13, which is why the outer diameter of the partial area 12a is smaller in contrast to Figure 3b.
  • the tools 20, 21 outlined in Figure 7 can be used for the injection molding of the cover plate 2 of the impeller 1.
  • the tool 21 forms the shape for the outer contour of the cover disk 2, while the tool 20 represents the shape for the inner contour of the cover disk 2.
  • the tool 21 is first clamped on a mandrel and the bearing ring 10 is inserted. After placing the second tool 20, the cavity formed between the tools 20, 21 is sprayed out, so that the cover plate with the back-injected bearing ring 10 is created at the suction mouth 4.
  • the stationary part of the mechanical seal consists of the stationary bearing ring 30, which is fixed in the axial direction by means of a bearing ring carrier 31.
  • the sectional view in Figure 6 shows the suction channel 40 in the pump housing 50.
  • the suction channel has a double stage with the first shoulder 41 and the second shoulder 42, which is located closer to the impeller, each of which is formed by a step increase in the diameter of the suction channel 40.
  • the stationary bearing ring 30 is mounted on an O-ring 32, whereby the bearing ring 30 can be moved slightly away from the impeller in order to be able to compensate for any deviations from the plane parallelism of the sliding surfaces 10a, 30a.
  • the bearing ring carrier 31 is then placed and fixed to the housing 50 in a rotationally fixed manner and immovably in the axial direction.
  • the bearing ring 30 lies in the axial direction between the impeller 1 and the pump housing 50.
  • Both bearing ring carrier 31 and bearing ring 30 have circular openings that are coaxial with one another.
  • the inner diameter of the bearing ring carrier 31 is chosen to be larger, so that the sliding surface 30a of the bearing ring 30 is exposed (see Figure 5).
  • the inner diameter of the bearing ring carrier 31 is selected to be larger than the outer diameter of the cylindrical suction mouth 4 of the impeller 1, so that the cylindrical projection 4a of the impeller can be accommodated in the inner diameter of the bearing ring carrier 31.
  • bearing ring carrier 31 is provided with axial grooves 33 which engage complementary projections 34 of the bearing ring 30 extending in the axial direction towards the impeller 1.
  • the sliding surface 10a of the rotating bearing ring 10 can either be designed as a continuous annular surface 10 (FIG. 1), alternatively the sliding surface 100a of the bearing ring 100 can also be provided with several radial grooves 110, which act as oscillating grooves for sufficient lubrication of the surfaces 100a and 30a sliding on one another care for.
  • the formation of the locating grooves 110 on the bearing ring 100 has another technical advantage.
  • the rotation of the bearing ring 100 causes a pumping effect due to the radial grooves 110, which creates a delivery flow that counteracts the pressure-related volume flow through the gap. Ideally, this reduces the pressure-related volume flow so that any hydraulic losses through the gap can be further minimized.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Abstract

L'invention concerne une pompe centrifuge comprenant au moins une roue de pompe et au moins un joint d'étanchéité rotatif disposé entre la roue de pompe et le carter de pompe pour étanchéifier l'espace de roue entre le côté aspiration et le côté pression de la pompe centrifuge, caractérisé en ce que les surfaces de glissement du joint d'étanchéité rotatif sont disposées l'une au-dessus de l'autre dans la direction axiale, de sorte que le joint d'étanchéité rotatif fonctionne comme un palier axial pour la roue de pompe.
PCT/EP2023/069695 2022-07-25 2023-07-14 Pompe centrifuge avec joint d'étanchéité rotatif pour l'étanchéification de l'espace de roue et procédé de fabrication d'une roue de pompe WO2024022850A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102022118557.5 2022-07-25
DE102022118557.5A DE102022118557A1 (de) 2022-07-25 2022-07-25 Kreiselpumpe mit Gleitringdichtung zur Abdichtung des Laufradspaltes sowie Verfahren zur Herstellung eines Pumpenlaufrades

Publications (1)

Publication Number Publication Date
WO2024022850A1 true WO2024022850A1 (fr) 2024-02-01

Family

ID=87418751

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2023/069695 WO2024022850A1 (fr) 2022-07-25 2023-07-14 Pompe centrifuge avec joint d'étanchéité rotatif pour l'étanchéification de l'espace de roue et procédé de fabrication d'une roue de pompe

Country Status (2)

Country Link
DE (1) DE102022118557A1 (fr)
WO (1) WO2024022850A1 (fr)

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4678399A (en) * 1984-03-01 1987-07-07 Hughes Tool Company Resistant components for submersible pump stages
DE102009009389A1 (de) * 2009-02-18 2010-08-19 Woco Industrietechnik Gmbh Verdichtergehäuse, Verdichter umfassend ein solches Verdichtergehäuse und Verfahren zur Herstellung eines Verdichtergehäuses
DE102012218861A1 (de) * 2012-10-16 2014-04-17 Mahle International Gmbh Pumpe
US9677560B1 (en) * 2014-07-11 2017-06-13 Summit Esp, Llc Centrifugal pump impeller support system and apparatus
DE102020003855A1 (de) * 2020-06-26 2021-12-30 KSB SE & Co. KGaA Kreiselpumpe zur Förderung feststoffhaltiger Medien

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102004024931A1 (de) 2004-05-19 2005-12-15 Siemens Ag Kreiselpumpe, die ein Laufrad und ein Spiralgehäuse aufweist
DE102016003180A1 (de) 2016-03-16 2017-09-21 Ksb Aktiengesellschaft Kreiselpumpe mit einer Anordnung zur Reduzierung einer Rückströmung
DE102019129494A1 (de) 2019-10-31 2021-05-06 Nidec Gpm Gmbh Kühlmittelpumpe mit verbesserter Spaltdichtung

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4678399A (en) * 1984-03-01 1987-07-07 Hughes Tool Company Resistant components for submersible pump stages
DE102009009389A1 (de) * 2009-02-18 2010-08-19 Woco Industrietechnik Gmbh Verdichtergehäuse, Verdichter umfassend ein solches Verdichtergehäuse und Verfahren zur Herstellung eines Verdichtergehäuses
DE102012218861A1 (de) * 2012-10-16 2014-04-17 Mahle International Gmbh Pumpe
US9677560B1 (en) * 2014-07-11 2017-06-13 Summit Esp, Llc Centrifugal pump impeller support system and apparatus
DE102020003855A1 (de) * 2020-06-26 2021-12-30 KSB SE & Co. KGaA Kreiselpumpe zur Förderung feststoffhaltiger Medien

Also Published As

Publication number Publication date
DE102022118557A1 (de) 2024-01-25

Similar Documents

Publication Publication Date Title
DE602004012654T2 (de) System zum Spritzgiessen von einem Kunststoffrotationskörper
EP1701038B1 (fr) Pompe à engrenages internes
EP2143954B1 (fr) Pompe
DE202011050101U1 (de) Getriebeanordnung und Rad davon
DE19710470A1 (de) Antriebsschneckeneinheit sowie die Einheit verwendender Elektromotor
DE10353566A1 (de) Strahlantrieb
DE4040200C2 (de) Kühlmittelpumpe zur Montage an dem Pumpengehäuse einer Brennkraftmaschine
EP1013926B1 (fr) Machine hydraulique à déplacement positif, en particulier pompe
EP0707686B1 (fr) Machine hydraulique a roues dentees (pompe ou moteur), notamment machine a roues dentees interieures
WO2024022850A1 (fr) Pompe centrifuge avec joint d'étanchéité rotatif pour l'étanchéification de l'espace de roue et procédé de fabrication d'une roue de pompe
EP0918932B1 (fr) Groupe motopompe electrique
WO2003036094A2 (fr) Pompe a vide
DE3211068A1 (de) Servolenkung
DE102004060554A1 (de) Flügelzellenpumpe
EP2002169B1 (fr) Pompe a lubrifiant ou pompe hydraulique
DE3045192C2 (de) Zahnradpumpe
EP4001665B1 (fr) Pompe centrifuge dotée d'un carter de pompe
DE102009000506A1 (de) Anpressvorrichtung
DE3820483A1 (de) Pumpe fuer viskose fluessigkeiten, insbesondere schmieroelpumpe
EP3441619B1 (fr) Pompe centrifuge
WO2009115142A1 (fr) Machine-outil à main, en particulier meuleuse à main
DE2641328A1 (de) Fluessigkeitspumpe
DE3519741C2 (fr)
EP0797736B1 (fr) Carter de pompe
DE2343630A1 (de) Rotierende verdraengerpumpe, insbesondere zahnradpumpe

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 23744129

Country of ref document: EP

Kind code of ref document: A1