EP3339654A1 - Pompe centrifuge - Google Patents

Pompe centrifuge Download PDF

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Publication number
EP3339654A1
EP3339654A1 EP16205241.9A EP16205241A EP3339654A1 EP 3339654 A1 EP3339654 A1 EP 3339654A1 EP 16205241 A EP16205241 A EP 16205241A EP 3339654 A1 EP3339654 A1 EP 3339654A1
Authority
EP
European Patent Office
Prior art keywords
sealing ring
sealing
impeller
centrifugal pump
pump according
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.)
Granted
Application number
EP16205241.9A
Other languages
German (de)
English (en)
Other versions
EP3339654B1 (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 CN201780077450.2A priority patent/CN110088480B/zh
Priority to US16/470,876 priority patent/US11280344B2/en
Priority to RU2019118974A priority patent/RU2730217C1/ru
Priority to PCT/EP2017/083121 priority patent/WO2018114709A1/fr
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
    • F04D29/165—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
    • F04D29/08—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
    • 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 against a fixed pump part by means of a sealing arrangement, wherein the seal assembly has 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 has a sealing lip which bears against the outside of the centrifugal wheel in the region of the suction mouth.
  • the sealing lip is arranged so that the contact pressure increases with increasing impeller speed, ie with increasing differential pressure between the pressure side and suction side of the impeller.
  • the invention according to the invention the task of a generic centrifugal pump in such a way that on the one hand the best possible sealing between the suction mouth and fixed pump part during operation of the pump and on the other hand, the lowest possible friction losses.
  • the centrifugal pump according to the invention has at least one pump stage, with a rotatable impeller, which forms a suction mouth, which by means of a fixed pump part a sealing arrangement is sealed, wherein the sealing arrangement comprises a sealing ring between the impeller and the stationary pump part.
  • the sealing arrangement is designed such that, viewed at least during the conveying operation of the pump in the circumferential direction of the sealing ring, it has alternately successively spaced-apart from the counter-sealing surface and sealing sections bearing against the counter-sealing surface.
  • the basic idea of this solution according to the invention is to run the sealing ring in the manner of a plain bearing, so that at least in the conveying operation of the pump, that is, when the impeller rotates relative to the fixed pump part, between the sealing ring and the surface against which this is applied, a liquid film is constructed and thus between the sealing ring and the counter-sealing surface fluid friction and no solid friction arises.
  • Such fluid friction minimizes the friction losses within the seal, but on the other hand allows to keep the fürströmbate within the seal assembly extremely low. Fluid friction not only significantly reduces friction within the seal assembly, it also minimizes wear on the seal itself.
  • a complete fluid friction must be ensured, as is the case with a slide bearing.
  • Intermediates between fluid friction and solid friction may also be provided in the solution according to the invention, that is to say that the spaced-apart surfaces of the sealing arrangement are provided for introducing friction-reducing fluid into the sealing gap between the sealing surface and the counter-sealing surface, but this does not necessarily mean complete fluid friction, but optionally also a mixed friction and operating state-dependent optionally a solid state friction can occur.
  • a punctual Contact be provided in the region between the spaced sealing surfaces.
  • the adjacent sealing portions are formed by the sealing ring itself.
  • the spaced sections which lie between the adjacent sealing portions, they can be formed either by the sealing ring itself but also by the suction mouth of the impeller by there, for example, recesses in the surface or other similar measures are provided.
  • the solution according to the invention can be used both in single-stage and multi-stage centrifugal pumps, in single-stage centrifugal pumps, the seal arrangement is typically between the suction port of the impeller and the housing, in multi-stage arrangements between the suction port and a fixed pump part typically a pump stage.
  • One or more stages may be provided with the seal arrangement according to the invention.
  • the gyroscope is preferably a radial or Halbaxialrad, that is a gyro, in which the suction port in the axial direction of the wheel and the downstream side is directed radially or axially / radially.
  • the invention is not limited in principle to this type.
  • the basic idea of the present invention namely to have successively fitting and non-adjoining sealing sections in order to ensure the construction of a liquid film between seal and counter-sealing surface, can not only be effected according to the invention by appropriate design of sealing surface and / or counter-sealing surface, but alternatively or additionally by An embodiment according to claim 2, wherein the sealing ring is at least partially elastic and the contact surface 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 form the sealing ring over its circumference with different stiffness and to arrange so that during operation of the pump, so when rotating the impeller against the fixed pump part, by the pressure difference between the pressure side and suction side, the hydraulic forces the sealing ring on his Press the circumference to different degrees against the counter-sealing surface. It is preferably provided according to the invention that the sealing ring is designed and arranged so that it is arranged at rest of the pump, so when the impeller stands still, spaced from the counter-sealing surface, in particular from the suction.
  • the latter arrangement also has the advantage that the seal, that is the concern of sealing ring sections on the counter-sealing surface only during operation and otherwise there is a significant distance between sealing ring and counter-sealing surface, whereby on the one hand a certain self-cleaning effect occurs and on the other hand, for example, a calcification of the sealing surfaces is counteracted as they are in motion.
  • a significant advantage results from the fact that the tolerances in the region of the sealing arrangement are such that the production and assembly is simplified and thus the manufacturing costs are reduced.
  • the hydraulic control in which sealing ring sections abut against the counter-sealing surface and others are spaced apart, can advantageously be effected in that the sealing ring has a different stiffness distributed over its circumference, preferably alternately stiff and less rigid sections, so that When concerns hydraulic forces the sealing ring is deliberately deformed to form adjacent sections and non-adjacent sections.
  • the sealing ring has on its outer circumference the cross-section weakening recesses, which preferably extend parallel to each other. These recesses, in which the material thickness is reduced, can be arranged parallel to the longitudinal central axis of the sealing ring or preferably obliquely thereto, so that the alternately successive sections, on which abut the sealing surface on the counter-sealing surface and on which they do not rest, seen in the axial direction are arranged overlapping.
  • the targeted material weakening can be effected not only by recesses on the outer circumference of the sealing ring, but also by recesses and / or on the inner circumference.
  • the arrangement of the sealing ring with respect to the suction mouth is to be considered.
  • the sealing ring is designed so that it rests against the outer circumference of the suction mouth, then the sealing ring is freely designable on its outer circumference, whereas recesses are to be dimensioned on the inner circumference so that no unacceptably high Kochströmbate occur.
  • the recesses on the inner circumference can be designed so that they leak to the suction side, so that there forms a narrow circumferential ring, which prevents overflow.
  • the sealing ring with its outer circumference sealingly abuts the suction mouth it may be advantageous to provide the recesses on the inner circumference of the sealing ring, which are suitably arranged parallel to each other, for example, axially parallel or obliquely thereto.
  • the recesses are seen in the circumferential direction wedge-shaped.
  • Such a design has in particular on the side of the sealing ring, which is intended to rest against the counter-sealing surface has the advantage that reliably build a fluid film by the lying in the direction of rotation wedge-shaped recesses that fill with liquid during operation, which a low-friction sliding of the Sealing ring ensures on the sealing surface.
  • the wedge-shaped recesses cause targeted material weakening, due to the wedge shape, the weakening material is not abruptly in both circumferential direction but abruptly in one direction only and rising in the other direction, thereby ensuring when pressurized that the Sealing ring deformed in the desired manner only at the desired locations.
  • the sealing ring can be designed exactly as for a particular Use case is particularly advantageous. It should be understood that while the seal assembly of the invention is effective and effective over a wide range of rotational speeds, typically the effectiveness is highest in a range of rotational speeds.
  • This range is expediently designed to be the speed range in which the centrifugal pump is likely to be operated most frequently.
  • the seal assembly designed so that it is most effective in the maximum pressure range of the pump. This makes sense insofar as the overflow losses in the highest pressure range are typically greatest in centrifugal pumps according to the prior art.
  • the sealing ring when the sealing ring is attached to the fixed pump part and is provided to seal against an outer surface of the impeller near the suction mouth is particularly advantageous.
  • the suction of the pump is not affected, in addition, at least when the sealing ring is arranged at a distance from the impeller, when starting it a kind of Venturi effect, whereby the pressure on the outside increases and the process that increases the sealing ring sections applied to the counter-sealing surface on the outer circumference of the impeller, is accelerated.
  • the arrangement is such that the outer circumference of the sealing ring is acted upon in operation with the pressure of the pressure side of the impeller, by which ultimately the application of the sealing ring is controlled to the impeller, in the same manner as the deformation of the sealing ring.
  • the sealing arrangement for the function of the sealing arrangement, as described initially, it basically does not matter whether the sealing ring is arranged on the housing side or the impeller side, but as a rule the housing arrangement, that is to say the arrangement on a fixed pump part be the cheaper, because then any imbalance of the sealing ring play no role and the moment of inertia of the impeller is not increased by the sealing ring.
  • the sealing ring on the impeller this preferably be arranged at the suction end of the impeller and a counter-sealing surface by a dipping into the sealing ring portion of the fixed pump part - if the seal is radial - or by an axial annular surface of the fixed pump part - when the seal takes place axially - are formed.
  • the annular surface lies in a plane transverse to the axis of rotation of the impeller, whereas in the case of radial sealing the annular 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, that is, if the sealing ring virtually forms the suction mouth, which is, however, moved due to the dipping fixed pump part of the function in the Kreiselradinnere.
  • the sealing ring in particular if the deformation described above is to be effected by hydraulic forces of the delivery fluid, it is essential that, in particular, the outer side is, if possible, fully loaded with the pressure of the pressure side of the centrifugal wheel.
  • 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 forms hydrostatic fluid film between the mutually moving surfaces of the seal assembly. Hydrodynamically this can be done by appropriate shaping of the sealing ring and / or its recesses, for example, wedge-shaped, hydrostatically, for example, provided in the sealing ring, leading to the pressure side channels, which open into the sealing surface. It can also be provided a combination of hydrodynamically and hydrostatically structured liquid film.
  • centrifugal pump has a fixed pump housing 1, which has a suction port 2 and a pressure port 3, in which a shaft 4 is rotatably mounted, which drives a seated thereon impeller 5, the axial suction port 6 is conductively connected to the suction port 2 and its Outflow side 7 is arranged radially and is line connected to the pressure port 3.
  • the pump housing 1 stands here for any fixed pump component, for example, in a multi-stage pump for the fixed part of a pump stage, that is, the basis of Fig. 1 illustrated schematic representation can also be transmitted to one or more arbitrary wheels with the corresponding fixed pump parts.
  • an overflow 8 is formed, which can be shut off by a sealing ring 9 in the pump.
  • Examples of the design of the seal arrangement between the suction mouth 6 of the centrifugal pump, ie the suction side and the overflow channel 8 connected to the pressure side are described in detail with reference to FIG Fig. 2 to 7 shown, which only schematically a part of this Overflow 8, the impeller 5, the pump housing 1 and the sealing ring 9 show.
  • sealing ring 9a which is arranged in the same way as the basis of Fig. 1 shown sealing ring 9, with a narrow end face, in Fig. 2 its lower side attached to the fixed part 1 of the pump. It has a slender annular cylindrical shape, wherein the inside of the sealing ring 9a is provided for engagement with the substantially cylindrical outer circumference in the region of the suction mouth 6 of the centrifugal wheel 5. In the unloaded state, the sealing ring 9 a is arranged at a small distance to the outside of the suction mouth 6 of the impeller 5.
  • the sealing ring 9a is constructed of elastic material and matched in material and size so that the gap formed between the inside of the sealing ring 9a and the outside of the suction 6 of the impeller 5 is closed during operation of the pump.
  • the system of the sealing ring 9a on the outside of the suction 6 is not fully, but only partially due to the different stiffness of the sealing ring 9a in the circumferential direction.
  • the inside of the sealing ring 9a is not circumferentially over the entire surface of the counter-sealing surface 11, but it follow in the circumferential direction on an adjacent sealing ring portion one of which spaced and then an adjacent, etc. alternately, over the entire circumference of the ring 9a.
  • FIG. 3 and 4 schematically shows how the housing side fixed sealing ring 9 from its static position ( Fig. 3 ), in which the gyroscope 5 stops, upon rotation of the gyroscope 5, first by the Venturi effect building up on the outside and then by the differential pressure between the pressure side and suction side against the sealing surface 11 of the gyroscope 5.
  • the application of the sealing ring 9 to the suction mouth 6, as it is in Fig. 4 is shown exclusively by hydraulic forces, so that at standstill of the impeller 5 of the sealing ring 9 in his in Fig. 3 repositioned starting position in which a gap between sealing surface 12 and counter-sealing surface 11 is formed in the overflow 8.
  • This elastic movement of the sealing ring 9 when applying or resetting cleans the sealing gap and ensures that, in particular, no deposits form on the sealing surface 12.
  • a sealing ring 9b is shown, which has a cross-sectionally L-shaped profile, wherein an upright leg 13 according to the Fig. 3 and 4 9 described, whereas a lying leg 14 for fixing the sealing ring 9b on the fixed part 1 of the pump, so for example the pump housing 1 is provided.
  • the attachment of the sealing ring 9b can be made cohesively and / or non-positively, in which the ring 9b is pressed into the corresponding recess of the pump housing 1.
  • a sealing ring 9c which has the shape of an annular disc and which is fixedly connected at its inner circumference with the outer circumference of the impeller 5 in the region of the suction 6.
  • the sealing ring 9c thus rotates with the impeller 5, its sealing surface 12 comes to rest on the mating surface 11 on the pump housing, in which case the differential pressure between the pressure side of the impeller and suction side for the partial contact of the sealing surface 12 on the mating surface 11 provides.
  • the sealing ring 9 c is not shown here by recesses over its circumference different stiffness, so that form portions of the sealing surface 12 which abut against the mating surface 11 and portions which are spaced therefrom. So that even with this arrangement, the above-described "sliding bearing effect" occurs, that is, a viable liquid film between sealing surface 12 and mating sealing surface 11 is formed.
  • the sealing ring 9d is arranged on the suction-side end face of the impeller 5 in extension of the suction 6.
  • a ring section 15 is provided, which is arranged within the sealing ring 9d and extends into the suction mouth 6 of the impeller 5.
  • the mating surface 11 for the sealing ring 9d is formed by the inside of this annular portion 15.
  • the sealing ring 9d may be formed in the same way as the basis of Fig. 2 described sealing ring 9a or as below with reference to the Fig. 8 and 9 described sealing rings.
  • a sealing ring 9e is provided Fig. 8 shows by way of example how such a sealing ring 9 of Fig. 3 and 4 , which may be made of elastic material such as rubber, silicone or the like, may be configured to achieve the effects described above.
  • the sealing ring 9e has distributed over its outer circumference a total of ten wedge-shaped recesses 16, the depth in representation according to Fig. 8 increase in the clockwise direction, that is deeper penetrate 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 likewise 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 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 this deforms selectively humpback when building a pressure from the outside on its inside, that forms sections that abut against the counter-sealing surface 11 and those which are spaced therefrom, serve the recesses 18 on the inner circumference primarily the formation of a viable lubricating film between the sealing surface 12, so the inside of the sealing ring 9e and the counter-sealing surface 11.
  • these can also influence the deformation of the sealing ring.
  • FIG. 9 An alternative embodiment of such a sealing ring 9f is based on Fig. 9 shown.
  • the structure of the sealing ring 9f made of an elastic material in which wedge-shaped recesses 16a on the outside alternate with cylindrical portions 17a and in which wedge-shaped recesses 18a alternate with cylindrical portions 19a on the inside differs from the above with reference to FIG Fig. 8 illustrated embodiment essentially in that the recesses 16a and 18a and the portions 17a and 19a are not parallel to the axis of the ring 9f but obliquely arranged, on the outside and on the inside in the same slope, so that adjacent and not abutting portions of the sealing ring 9f result when pressurized from the outside, which overlap seen in the axial direction.
  • the above embodiments may not be used to reflect the various possibilities of sealing ring designs that result from the present invention. It must be determined experimentally and / or computationally in individual cases, how to establish a viable liquid film between the sealing ring and the counter-sealing surface and over as large a speed range of the pump to keep wear and friction losses on the seal as small as possible.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
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
CN201780077450.2A CN110088480B (zh) 2016-12-20 2017-12-15 离心泵
US16/470,876 US11280344B2 (en) 2016-12-20 2017-12-15 Centrifugal pump
RU2019118974A RU2730217C1 (ru) 2016-12-20 2017-12-15 Центробежный насос (варианты)
PCT/EP2017/083121 WO2018114709A1 (fr) 2016-12-20 2017-12-15 Pompe centrifuge

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

Family

ID=57570781

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)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN114087227A (zh) * 2021-12-22 2022-02-25 上海阿波罗智能装备科技有限公司 一种用于离心泵组的可调节密封环

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2644403A (en) * 1952-03-05 1953-07-07 Ingersoll Rand Co Device for preventing clogging in centrifugal pumps
US3020850A (en) * 1958-02-27 1962-02-13 Meckum Engineering Inc Dredge pump seal
US5984629A (en) * 1993-09-25 1999-11-16 Ksb Aktiengesellscaft Turbo-machine with reduced abrasive wear
CN2486751Y (zh) 2001-07-06 2002-04-17 李济民 带弹性密封环的泵
US20070160465A1 (en) * 2006-01-10 2007-07-12 Roudnev Aleksander S Flexible floating ring seal arrangement for rotodynamic pumps
DE102014116466B3 (de) 2014-11-11 2015-12-10 Uwe Würdig Saugseitige Spaltabdichtung bei einer Kreiselpumpe

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6109617A (en) * 1998-03-04 2000-08-29 Power Packing Co., Inc. Gas seal assembly and method of sealing
US6460635B1 (en) * 1999-10-25 2002-10-08 Kalsi Engineering, Inc. Load responsive hydrodynamic bearing
RU2196254C2 (ru) * 2001-02-14 2003-01-10 Открытое акционерное общество "Борец" Центробежный насос
US9004494B2 (en) * 2006-04-05 2015-04-14 Dean Foote Rotary seal for dynamically sealing against a surface of a shaft
EP2148096B1 (fr) * 2008-07-25 2013-04-10 Grundfos Management A/S Pompe centrifuge
US9010373B2 (en) * 2010-09-09 2015-04-21 Mac Valves, Inc. Pressure balanced valve with diaphragm valve member end seal
US9903477B2 (en) * 2013-08-28 2018-02-27 Dresser-Rand Company Self-centering labyrinth seal
JP6392343B2 (ja) * 2014-06-26 2018-09-19 イーグル工業株式会社 摺動部品
CN104235380A (zh) * 2014-08-29 2014-12-24 江苏大学 一种具有双级错列流体动压槽机械密封

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2644403A (en) * 1952-03-05 1953-07-07 Ingersoll Rand Co Device for preventing clogging in centrifugal pumps
US3020850A (en) * 1958-02-27 1962-02-13 Meckum Engineering Inc Dredge pump seal
US5984629A (en) * 1993-09-25 1999-11-16 Ksb Aktiengesellscaft Turbo-machine with reduced abrasive wear
CN2486751Y (zh) 2001-07-06 2002-04-17 李济民 带弹性密封环的泵
US20070160465A1 (en) * 2006-01-10 2007-07-12 Roudnev Aleksander S Flexible floating ring seal arrangement for rotodynamic pumps
DE102014116466B3 (de) 2014-11-11 2015-12-10 Uwe Würdig Saugseitige Spaltabdichtung bei einer Kreiselpumpe

Also Published As

Publication number Publication date
US20190323513A1 (en) 2019-10-24
US11280344B2 (en) 2022-03-22
EP3339654B1 (fr) 2021-03-03
CN110088480B (zh) 2021-08-31
WO2018114709A1 (fr) 2018-06-28
RU2730217C1 (ru) 2020-08-19
CN110088480A (zh) 2019-08-02

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