EP3339654B1 - Pompe centrifuge - Google Patents

Pompe centrifuge Download PDF

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Publication number
EP3339654B1
EP3339654B1 EP16205241.9A EP16205241A EP3339654B1 EP 3339654 B1 EP3339654 B1 EP 3339654B1 EP 16205241 A EP16205241 A EP 16205241A EP 3339654 B1 EP3339654 B1 EP 3339654B1
Authority
EP
European Patent Office
Prior art keywords
sealing ring
sealing
impeller
recesses
centrifugal pump
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
EP16205241.9A
Other languages
German (de)
English (en)
Other versions
EP3339654A1 (fr
Inventor
Brian Lundsted Poulsen
Lasse Søgaard LEDET
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.)
Grundfos Holdings AS
Original Assignee
Grundfos Holdings AS
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 Grundfos Holdings AS filed Critical Grundfos Holdings AS
Priority to EP16205241.9A priority Critical patent/EP3339654B1/fr
Priority to PCT/EP2017/083121 priority patent/WO2018114709A1/fr
Priority to RU2019118974A priority patent/RU2730217C1/ru
Priority to US16/470,876 priority patent/US11280344B2/en
Priority to CN201780077450.2A priority patent/CN110088480B/zh
Publication of EP3339654A1 publication Critical patent/EP3339654A1/fr
Application granted granted Critical
Publication of EP3339654B1 publication Critical patent/EP3339654B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • F04D29/161—Sealings between pressure and suction sides especially adapted for elastic fluid 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
    • F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D17/08—Centrifugal 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
    • F04D29/08—Sealings
    • F04D29/16—Sealings between pressure and suction sides
    • 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
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2240/00—Components
    • F05B2240/57—Seals

Definitions

  • the invention relates to a centrifugal pump with at least one pump stage, with a rotatable impeller with a suction mouth, which is sealed off from a stationary pump part by means of a sealing arrangement, the sealing arrangement having a sealing ring between the impeller and the stationary pump part.
  • a centrifugal pump in which a sealing ring is arranged on the housing side in the region of the suction mouth of the pump, which sealing ring has a sealing lip which rests on the outside of the impeller in the region of the suction mouth.
  • the sealing lip is arranged in such a way that the contact pressure increases with increasing impeller speed, i.e. with increasing differential pressure between the pressure side and suction side of the impeller.
  • the off is cheaper DE 10 2014 116 466 B3 known sealing arrangement in which a special sliding surface is provided on the suction mouth side on the outer circumference of the impeller and a sealing ring is incorporated on the housing side, which with one edge of its free End rests against this sliding surface.
  • a special sliding surface is provided on the suction mouth side on the outer circumference of the impeller and a sealing ring is incorporated on the housing side, which with one edge of its free End rests against this sliding surface.
  • the sealing of the suction mouth against the stationary pump part by means of a sealing arrangement reduces the overflow losses, but increases the friction losses within the pump, so that the requirements for a high sealing effect on the one hand and low friction losses on the other hand are contrary.
  • only the sealant-free reduction of the gap between the suction mouth and the stationary pump part is more favorable, but this increases the manufacturing tolerances and thus the manufacturing costs.
  • the invention according to the application is based on the object of designing a generic centrifugal pump in such a way that, on the one hand, the best possible seal between the suction mouth and the stationary pump part during operation of the pump and, on the other hand, the lowest possible friction losses.
  • the basic idea of this solution according to the invention is to let the sealing ring run like a plain bearing so that at least when the pump is in delivery mode, i.e. when the impeller rotates relative to the stationary pump part, a film of liquid between the sealing ring and the surface on which it rests is built up and thus fluid friction and no solid body friction occurs between the sealing ring and the mating sealing surface.
  • Such fluid friction minimizes the friction losses within the seal, but on the other hand allows the overflow losses within the seal arrangement to be kept extremely low. Fluid friction not only significantly reduces the friction within the seal arrangement, but also reduces wear on the seal itself to a minimum.
  • complete fluid friction does not necessarily have to be guaranteed, as is the case with a plain bearing.
  • intermediate stages between fluid friction and solid-state friction can also be provided, that is to say that the spaced-apart surfaces of the sealing arrangement are intended to introduce friction-reducing fluid into the sealing gap between the sealing surface and the counter-sealing surface, but that there is not necessarily complete fluid friction, but possibly also mixed friction and, depending on the operating state, solid body friction can also occur.
  • punctiform contact can be provided in the area between the sealing surfaces that are spaced apart from one another.
  • the solution according to the invention can be used with single-stage as well as multi-stage centrifugal pumps, with single-stage centrifugal pumps the sealing arrangement is typically between the suction mouth of the impeller and the housing, with multi-stage arrangements between the suction mouth and a stationary pump part typically a pump stage.
  • One or more stages can be provided with the sealing arrangement according to the invention.
  • the centrifugal wheel is preferably a radial or semi-axial wheel, that is to say a centrifugal wheel in which the suction mouth is directed in the axial direction of the wheel and the outflow side is directed radially or axially / radially. In principle, however, the invention is not limited to this type of construction.
  • the basic idea of the present invention namely to have successively abutting and non-abutting sealing sections in order to ensure the build-up of a liquid film between the seal and the mating sealing surface, can be achieved according to the invention by an embodiment according to claim 1, in which the sealing ring is at least partially elastic and the System of the sealing ring or the sealing ring sections on the mating surface is controlled by the hydraulic forces on the pressure side of the impeller.
  • the basic idea of this solution is to design the sealing ring with different stiffnesses over its circumference and to arrange it in such a way that when the pump is operating, i.e. when the impeller is rotating in relation to the stationary pump part, the hydraulic forces affect the sealing ring through the pressure difference between the pressure side and suction side Press the circumference to different degrees on the counter-sealing surface. It is preferably provided according to the invention that the sealing ring is designed and arranged so that it is in the idle state of the pump, that is, when the impeller is at a standstill Counter sealing surface, in particular is arranged spaced from the suction mouth.
  • the sealing ring sections in contact with the counter-sealing surface only takes place during operation and there is also a clear gap between the sealing ring and the counter-sealing surface, which on the one hand results in a certain self-cleaning effect and on the other hand, for example, calcification of the sealing surfaces is counteracted, as these are in motion.
  • the tolerances in the area of the sealing arrangement are such that manufacture and assembly are simplified and thus the manufacturing costs are reduced.
  • sealing ring sections rest against the mating sealing surface and others are spaced apart, and this alternately, is achieved in that the sealing ring has a different stiffness distributed over its circumference, preferably alternately stiff and less stiff sections, so that when in contact hydraulic forces, the sealing ring is deliberately deformed to form adjacent sections and non-adjacent sections.
  • the sealing ring has recesses on its outer circumference which weaken the cross section and which preferably extend parallel to one another. These recesses, in which the material thickness is reduced, can be arranged parallel to the longitudinal center axis of the sealing ring or also preferably at an angle to it, so that the alternately successive sections, on which the sealing surface abuts the counter-sealing surface and which they do not abut, are arranged overlapping viewed in the axial direction .
  • the targeted material weakening can not only be brought about by recesses on the outer circumference of the sealing ring, but also by recesses on the inner circumference.
  • the arrangement of the sealing ring in relation to the suction mouth must be taken into account.
  • the sealing ring is designed so that it rests against the outer circumference of the suction mouth, then the sealing ring can be freely designed on its outer circumference, whereas recesses on the inner circumference must be dimensioned so that no inadmissibly high overflow losses occur.
  • the recesses on the inner circumference can be designed in such a way that they run out towards the suction side, so that a narrow circumferential ring is formed there, which prevents overflow.
  • the recesses are wedge-shaped as seen in the circumferential direction.
  • Such a design has the advantage, in particular on the side of the sealing ring, which is intended to rest on the counter-sealing surface, that a liquid film is reliably created due to the wedge-shaped recesses in the direction of rotation that fill with conveyed liquid during operation is built up, which ensures low-friction sliding of the sealing ring on the mating sealing surface.
  • the wedge-shaped recesses cause targeted material weakening, whereby due to the wedge shape the material weakening does not occur abruptly in both circumferential directions but only abruptly in one direction and increasing in the other direction, which ensures that the Sealing ring deformed in the desired way only in the desired places.
  • the sealing ring can be designed exactly as it is particularly advantageous for a specific application. It goes without saying that the sealing arrangement according to the invention is effective and effective for a wide speed range, but that the effectiveness is typically highest in a certain speed range.
  • This range is expediently designed so that it is the speed range in which the centrifugal pump is likely to be operated most frequently.
  • it can also be provided according to the invention to design the sealing arrangement in such a way that it is most effective in the maximum pressure range of the pump. This is useful insofar as the overflow losses in centrifugal pumps according to the state of the art are typically greatest in the maximum pressure range.
  • the sealing ring is attached to the stationary pump part and is provided for sealing against an outer surface of the impeller close to the suction mouth.
  • the suction area of the pump is not affected, and at least when the sealing ring is arranged at a distance from the impeller, a kind of Venturi effect occurs when it starts up, which increases the pressure on the outside and causes the sealing ring to move in sections against the mating sealing surface on the outer circumference of the impeller, is accelerated.
  • the arrangement is such that the outer circumference of the sealing ring is subjected to the pressure of the pressure side of the impeller during operation, which ultimately controls the application of the sealing ring to the impeller, in the same way as the deformation of the sealing ring.
  • the sealing ring is arranged on the housing side or on the impeller side, but as a rule the housing arrangement, i.e. the arrangement on a stationary pump part the more favorable, since any imbalances in the sealing ring then play no role and the mass moment of inertia of the impeller is not increased by the sealing ring.
  • the sealing ring when it is arranged on the impeller, it can preferably be arranged on the suction-side end of the impeller and a counter-sealing surface by an annular section of the stationary pump part that dips into the sealing ring - if the seal takes place radially
  • the ring section is formed by a cylindrical surface arranged parallel to the axis of rotation.
  • the sealing ring is arranged to continue the suction mouth of the impeller, i.e. if the sealing ring forms the suction mouth, which, however, is functionally displaced into the inside of the impeller due to the immersing fixed pump part. It is essential for the sealing ring that the pressure of the pressure side of the impeller is applied completely to the outside in particular, if possible.
  • the core idea of the solution according to the invention is to design the sealing ring in such a way that, during operation, a hydrodynamic or hydrostatic liquid film is formed between the surfaces of the sealing arrangement that are moved relative to one another. Hydrodynamically, this can be done by appropriate shaping of the sealing ring and / or its recesses, for example wedge-shaped, and hydrostatically, for example, through channels which are provided in the sealing ring and lead to the pressure side and open into the sealing surface. A combination of hydrodynamically and hydrostatically built up liquid film can also be provided.
  • the centrifugal pump shown in a highly simplified manner has a stationary pump housing 1, which has a suction connection 2 and a pressure connection 3, in which a shaft 4 is rotatably mounted, which drives a centrifugal wheel 5 seated on it, the axial suction mouth 6 of which is line-connected to the suction connection 2 and whose The outflow side 7 is arranged radially and line-connected to the pressure connection 3.
  • the pump housing 1 stands for any fixed pump component, for example in the case of a multi-stage pump for the fixed part of a pump stage, that is, that based on Fig. 1
  • the schematic representation shown can also be transferred to one or more impellers with the corresponding stationary pump parts.
  • an overflow channel 8 is formed which can be shut off by a sealing ring 9 in the pump.
  • Examples of the configuration of the sealing arrangement between the suction mouth 6 of the centrifugal pump, that is to say the suction side and the overflow channel 8 connected to the pressure side, are shown in detail on the basis of FIG Figures 2 to 7 which only schematically show a part of this overflow channel 8, the impeller 5, the pump housing 1 and the sealing ring 9.
  • the based on Fig. 2 illustrated sealing ring 9a, which is arranged in the same way as that based on Fig. 1
  • the sealing ring 9 shown has a narrow end face, in Fig. 2 its lower side attached to the fixed part 1 of the pump. It has a slim ring-cylindrical shape, the inside of the sealing ring 9a being intended to rest on the outer circumference, which is essentially cylindrical there, in the area of the suction mouth 6 of the impeller 5. In the unloaded state, the sealing ring 9a is arranged at a small distance from the outside of the suction mouth 6 of the impeller 5.
  • the sealing ring 9a has recesses 10 distributed over its outer circumference, which are provided here parallel to one another and parallel to the longitudinal axis of the sealing ring 9a at a regular angular spacing on the outer circumference.
  • the material of the sealing ring 9a is weakened by these recesses 10, which have a partially circular cross-section, so that the sealing ring 9a has the smallest material thickness at the base of a recess 10 and the greatest material thickness at the edge of the recess 10.
  • the sealing ring 9a is made of elastic material and so material and Matched in size so that the gap formed between the inside of the sealing ring 9a and the outside of the suction mouth 6 of the impeller 5 is closed when the pump is in operation.
  • the sealing ring 9a does not rest on the outside of the suction mouth 6 over the entire circumference, but only in sections due to the different rigidity of the sealing ring 9a in the circumferential direction.
  • the inside of the sealing ring 9a does not fully lie against the mating sealing surface 11, but instead a sealing ring section which is spaced therefrom follows in the circumferential direction and then another adjacent sealing ring section alternately over the entire circumference of the ring 9a.
  • conveying liquid passes through the overflow channel 8 into the area between the sealing ring 9a and the counter-sealing surface 11, which is distributed over the sealing surface by the alternating contacting and non-contacting sections and the rotation of the impeller, so that in the area between the sealing ring 9a and counter sealing surface 11 there is always fluid friction.
  • Fig. 3 and 4th Based on Fig. 3 and 4th is shown schematically how the sealing ring 9 attached to the housing can move out of its static position ( Fig. 3 ), in which the impeller 5 stands still, initially due to the Venturi effect building up on the outside when the impeller 5 rotates then applied to the counter-sealing surface 11 of the impeller 5 by the differential pressure between the pressure side and the suction side.
  • the structure described with recesses 10 on the outer circumference of the sealing ring 9a can be used in order to generate alternately abutting and non-abutting sections between the sealing surface 12 and the counter-sealing surface 11.
  • recesses can be provided in the surface in the sealing surface 12 or in the counter-sealing surface 11, which recesses support this effect.
  • This elastic movement of the sealing ring 9 when it is applied or reset cleans the sealing gap and ensures that no deposits form on the sealing surface 12 in particular.
  • a sealing ring 9b which has an L-shaped profile in cross-section, with an upright leg 13 based on the Fig. 3 and 4th Sealing ring 9 described corresponds to, whereas a lying leg 14 is provided for fastening the sealing ring 9b to the stationary part 1 of the pump, that is to say, for example, the pump housing 1.
  • the fastening of the sealing ring 9b can take place in a cohesive and / or non-positive manner in that the ring 9b is pressed into the corresponding recess in the pump housing 1.
  • FIG. 6 When using Fig. 6
  • the embodiment variant shown (not belonging to the invention) is provided with a sealing ring 9c which has the shape of an annular disk and which is firmly connected on its inner circumference to the outer circumference of the impeller 5 in the area of the suction mouth 6.
  • the sealing ring 9c thus rotates with the impeller 5, its sealing surface 12 comes into contact with the counter-sealing surface 11 on the pump housing, whereby the differential pressure between the pressure side of the impeller and the suction side ensures that the sealing surface 12 contacts the counter-sealing surface 11 in sections.
  • the sealing ring 9c has different stiffnesses over its circumference due to recesses not shown here, so that sections of the sealing surface 12 are formed that bear against the counter-sealing surface 11 and sections that are spaced therefrom. So that the above-described “sliding bearing effect" also occurs with this arrangement, that is to say a stable liquid film is formed between the sealing surface 12 and the counter-sealing surface 11.
  • the sealing ring 9d is arranged on the suction-side end face of the impeller 5 as an extension of the suction mouth 6.
  • a ring section 15 is provided, which is arranged inside the sealing ring 9d and extends into the suction mouth 6 of the impeller 5.
  • the counter-sealing surface 11 for the sealing ring 9d is formed by the inside of this ring section 15.
  • the sealing ring 9d can be designed in the same way as that based on FIG Fig. 2 described sealing ring 9a or like the one below with reference to the Fig. 8 and 9 described sealing rings.
  • FIG. 8 shows an example of how such a sealing ring 9 of FIG Fig. 3 and 4th , which consists of elastic material, for example rubber, silicone or the like, can be configured to the previously described To achieve effects.
  • the sealing ring 9e has a total of ten wedge-shaped recesses 16 distributed over its outer circumference, the depth of which is shown in FIG Fig. 8 increase clockwise, i.e. penetrate deeper into the base material of the ring.
  • These wedge-shaped recesses 16 alternate with sections 17 which form part of a cylinder surface.
  • the sealing ring 9e has wedge-shaped recesses 18 which are interrupted by cylindrical sections 19 which also lie on a common cylinder surface.
  • the recesses 18 on the inside extend approximately only over a third of the circumference of the recesses 16 on the outside and over a smaller depth.
  • the direction of the wedge shape of the recesses 18 is opposite to the direction of the recesses 16.
  • the recesses 16 are used exclusively for the targeted weakening of the ring material, so that when a pressure builds up from the outside it is deliberately deformed in a bumpy manner on its inside, that is, forms sections that lie against the mating sealing surface 11 and those that are spaced from it, the recesses serve 18 on the inner circumference primarily the formation of a stable lubricating film between the sealing surface 12, that is to say the inside of the sealing ring 9e and the counter-sealing surface 11. However, these can also have an influence on the deformation of the sealing ring.
  • FIG. 9 An alternative embodiment of such a sealing ring 9f is based on Fig. 9 shown.

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

Claims (12)

  1. Pompe centrifuge comprenant au moins un étage de pompe, avec une turbine (5) adaptée pour être mise en rotation et ayant une bouche d'aspiration (6) qui est rendue étanche, par rapport à une partie de pompe statique (1), à l'aide d'un agencement de joint d'étanchéité, l'agencement de joint d'étanchéité comprenant un joint d'étanchéité (9) entre la turbine (5) et la partie de pompe statique (1), et le joint d'étanchéité (9), au moins par tronçons, étant formé de façon élastique et la surface d'appui (12) du joint d'étanchéité (9) ou des tronçons de joint d'étanchéité étant commandée à la surface opposée (11), par les forces hydrauliques, du côté pression de la turbine (5), le joint d'étanchéité (9a, 9e, 9f) comprenant, reparties sur son pourtour, des tronçons de rigidités différentes, caractérisée en ce que le joint d'étanchéité (9a, 9e, 9f) comprend, sur son pourtour extérieur, des évidements (10, 16, 16a) réduisant la section transversale.
  2. Pompe centrifuge selon la revendication 1, caractérisée en ce que les évidements (10, 16, 16a) sur le pourtour extérieur du joint d'étanchéité (9a, 9e, 9f) s'étendent parallèlement les uns aux autres.
  3. Pompe centrifuge selon une des revendications précédentes, caractérisée en ce que le joint d'étanchéité (9e, 9f) comprend, sur son pourtour intérieur, des évidements (18, 18a) réduisant la section transversale, qui s'étendent de préférence parallèlement les uns aux autres.
  4. Pompe centrifuge selon la revendication 2 ou 3, caractérisée en ce que les évidements (10, 16, 16a, 18, 18a) s'étendent parallèlement à la direction axiale du joint d'étanchéité ou obliquement par rapport à celle-ci.
  5. Pompe centrifuge selon l'une des revendications précédentes, caractérisée en ce que les évidements (16, 16a, 18, 18a) sont formés de manière cunéiforme dans la direction du pourtour.
  6. Pompe centrifuge selon l'une des revendications précédentes 2 à 5, caractérisée en ce que les évidements sont aussi bien ouverts vers le côté pression que vers le côté aspiration.
  7. Pompe centrifuge selon la revendication 5 ou 6, caractérisée en ce que les évidements cunéiformes (16, 16a) sur le pourtour extérieur et les évidements cunéiformes (18, 18a) sur le pourtour intérieur sont orientés de manière opposée et de préférence disposés de manière décalée les uns par rapport aux autres.
  8. Pompe centrifuge selon l'une des revendications précédentes, caractérisée en ce que le joint d'étanchéité (9, 9a, 9b) est disposé à la partie de pompe (1) statique et, pour l'étanchéité par rapport à une surface extérieure de la turbine (5), près de la bouche d'aspiration (6).
  9. Pompe centrifuge selon l'une des revendications précédentes, caractérisée en ce que le joint d'étanchéité (9d) est disposé à la turbine (5), de préférence à l'extrémité côté aspirant de la turbine (5) et qu'une surface opposée d'étanchéité (11) est formée par une partie d'anneau (15) de la partie de pompe (1) statique, plongeant dans le joint d'étanchéité (9d).
  10. Pompe centrifuge selon l'une des revendications précédentes, caractérisée en ce que le joint d'étanchéité (9d) est disposé à la turbine (5), de préférence à l'extrémité côté aspirant de la turbine (5) et qu'une surface opposée d'étanchéité (11) est formée par une surface en forme d'anneau de la partie de pompe (1) statique.
  11. Pompe centrifuge selon l'une des revendications précédentes, caractérisée en ce que le joint d'étanchéité (9d) est disposé en continuation de la bouche d'aspiration (6) de la turbine (5).
  12. Pompe centrifuge selon l'une des revendications précédentes, caractérisée en ce que le joint d'étanchéité (9) est formé de manière telle que, en marche, il se forme un film de liquide hydrodynamique ou hydrostatique entre les surfaces (11, 12) en mouvement l'une par rapport à l'autre de l'agencement de joint d'étanchéité.
EP16205241.9A 2016-12-20 2016-12-20 Pompe centrifuge Active EP3339654B1 (fr)

Priority Applications (5)

Application Number Priority Date Filing Date Title
EP16205241.9A EP3339654B1 (fr) 2016-12-20 2016-12-20 Pompe centrifuge
PCT/EP2017/083121 WO2018114709A1 (fr) 2016-12-20 2017-12-15 Pompe centrifuge
RU2019118974A RU2730217C1 (ru) 2016-12-20 2017-12-15 Центробежный насос (варианты)
US16/470,876 US11280344B2 (en) 2016-12-20 2017-12-15 Centrifugal pump
CN201780077450.2A CN110088480B (zh) 2016-12-20 2017-12-15 离心泵

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP16205241.9A EP3339654B1 (fr) 2016-12-20 2016-12-20 Pompe centrifuge

Publications (2)

Publication Number Publication Date
EP3339654A1 EP3339654A1 (fr) 2018-06-27
EP3339654B1 true EP3339654B1 (fr) 2021-03-03

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP16205241.9A Active EP3339654B1 (fr) 2016-12-20 2016-12-20 Pompe centrifuge

Country Status (5)

Country Link
US (1) US11280344B2 (fr)
EP (1) EP3339654B1 (fr)
CN (1) CN110088480B (fr)
RU (1) RU2730217C1 (fr)
WO (1) WO2018114709A1 (fr)

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RU2196254C2 (ru) * 2001-02-14 2003-01-10 Открытое акционерное общество "Борец" Центробежный насос

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CN110088480B (zh) 2021-08-31
US11280344B2 (en) 2022-03-22
RU2730217C1 (ru) 2020-08-19
CN110088480A (zh) 2019-08-02
US20190323513A1 (en) 2019-10-24
WO2018114709A1 (fr) 2018-06-28

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