EP3268616A1 - Pompe auto-aspirante - Google Patents

Pompe auto-aspirante

Info

Publication number
EP3268616A1
EP3268616A1 EP16709450.7A EP16709450A EP3268616A1 EP 3268616 A1 EP3268616 A1 EP 3268616A1 EP 16709450 A EP16709450 A EP 16709450A EP 3268616 A1 EP3268616 A1 EP 3268616A1
Authority
EP
European Patent Office
Prior art keywords
impeller
pump
shaft
shaft portion
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
EP16709450.7A
Other languages
German (de)
English (en)
Other versions
EP3268616B1 (fr
Inventor
Stephan Dirks
Markus Pawlik
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.)
GEA Tuchenhagen GmbH
Original Assignee
GEA Tuchenhagen GmbH
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
Family has litigation
First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=55524353&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=EP3268616(A1) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Application filed by GEA Tuchenhagen GmbH filed Critical GEA Tuchenhagen GmbH
Priority to PL16709450T priority Critical patent/PL3268616T3/pl
Publication of EP3268616A1 publication Critical patent/EP3268616A1/fr
Application granted granted Critical
Publication of EP3268616B1 publication Critical patent/EP3268616B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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
    • F04D1/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D1/06—Multi-stage 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
    • F04D29/043—Shafts
    • 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
    • F04D29/2277—Rotors specially for centrifugal pumps with special measures for increasing NPSH or dealing with liquids near boiling-point
    • 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
    • F04D29/60—Mounting; Assembling; Disassembling
    • F04D29/62—Mounting; Assembling; Disassembling of radial or helico-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
    • F04D3/00—Axial-flow pumps
    • F04D3/02—Axial-flow pumps of screw type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D9/00—Priming; Preventing vapour lock
    • F04D9/02—Self-priming 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
    • F04D9/00—Priming; Preventing vapour lock
    • F04D9/04—Priming; Preventing vapour lock using priming pumps; using booster pumps to prevent vapour-lock
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D9/00—Priming; Preventing vapour lock
    • F04D9/04—Priming; Preventing vapour lock using priming pumps; using booster pumps to prevent vapour-lock
    • F04D9/041—Priming; Preventing vapour lock using priming pumps; using booster pumps to prevent vapour-lock the priming pump having evacuating action

Definitions

  • the invention relates to a self-priming pump according to the preamble of claim 1.
  • Self-priming pumps are well known in the art and have been used successfully in the process industry for many years.
  • Process industry means in particular the beverage technology, food technology, pharmacy and
  • Such pumps are designed, for example, as self-priming centrifugal pumps. Between the inlet and outlet of such a centrifugal pump, a first
  • Chamber and a second chamber may be provided, in each of which an impeller is arranged.
  • Each impeller is part of a pumping stage, with the pumping stage closer to the inlet producing the self-priming property.
  • a first self-priming centrifugal pump of this type is proposed in EP 1 191 228 A2. Another self-priming centrifugal pump is shown in DE 10 2007 032 228 A1.
  • Liquid ring pumping stage which receives fluid to be pumped directly from the inlet of the centrifugal pump. By means of the liquid ring pumping stage, a negative pressure can be generated, which sucks fluid from the line connected to the inlet.
  • a return line connects the overpressure region of the centrifugal pumping stage to the inlet of the liquid ring pumping stage.
  • the impeller of the centrifugal pumping stage is connected to the impeller of the liquid ring pumping stage via a shaft portion which passes through an opening of a housing wall.
  • the shaft portion is designed to be cylindrical up to its impeller of the centrifugal pump facing shaft end.
  • NPSH Net Positive Suction Head
  • Haitruckière This parameter indicates which overpressure of the fluid to be pumped at the inlet of the pump must prevail above the vapor pressure of this fluid in order to avoid cavitation inside the pump. This pressure increase must be generated in the process plant. Therefore, a pump is sought, which has the lowest possible NPSH value. It is therefore an object of the invention to provide a self-priming pump with an improved Haitesruck Hab.
  • the self-priming pump has a housing with an inlet and an outlet.
  • a first impeller has a first pump portion disposed in a first chamber.
  • a second impeller carries a second pump section which is arranged in a second chamber. Between the pump sections, a shaft section is provided, which shaft section comprises a shaft end and passes through an opening of a housing wall. The flow of the fluid to be pumped, in particular a liquid with gas fractions, along the
  • Shaft portion is improved by the shaft portion between a constriction and the shaft end is tapered from the shaft end to the constriction and the first impeller and shaft portion between the constriction and the first pumping portion have a smooth course.
  • the flow path between the shaft sections is improved when the thinnest point of the shaft section is arranged in the second chamber.
  • the pump has a structurally simple drive, if according to another
  • first impeller and second impeller are mounted together flying.
  • Shaft section is formed on the second impeller.
  • the shaft portion is therefore shaped so as to receive a threaded portion of a drive shaft supporting the first impeller. This is an advantageous simple structure, which also deepens the advantages in terms of a modular system.
  • An embodiment of the pump according to the invention is that the first impeller has a first clamping surface, which cooperates with a second clamping surface, which is formed on the second impeller, and via the clamping surfaces a clamping force for clamping the first impeller on a truncated cone, which is formed on a drive shaft carrying the first impeller, is introduced into the first impeller.
  • This is a simple, inexpensive construction, which advantageously simultaneously causes the attachment of both wheels.
  • the second impeller comprises a blade arranged in a thread-like manner on a cylinder. This means a simple, cost-effective production of the second impeller, for example according to DE 20 2004 013 752 U1.
  • the pumping stage with the at least one thread-like blade can be additionally improved in its pumping action, the blade at her the
  • Shaft portion facing end has an extension.
  • an advantageous embodiment is a pump in which the second impeller is part of a liquid ring pumping stage.
  • the vortex formation in the pumped fluid is advantageously reduced, whereby the occurrence of cavitation is also reduced when the pump is so
  • Fig. 1 Perspective view of a self-priming centrifugal pump
  • Fig. 4 Perspective view of the second impeller.
  • Fig. 1 is a self-priming centrifugal pump 1 in a perspective
  • This centrifugal pump 1 comprises a liquid ring pumping stage 2 and a normal suction centrifugal pump 3.
  • the liquid ring pumping stage 2 is associated with an inlet 4 of the self-priming centrifugal pump 1.
  • Fluid, in particular liquid, which is possibly admixed with gas, enters through the inlet 4 of the centrifugal pump 1 and first enters the liquid ring pumping stage 2.
  • Centrifugal pump 1 A return line 6 branches off from the centrifugal pump 3. Fluid flows through this return line 6 from the centrifugal pump 1 back into the
  • Liquid ring pumping stage 2 and is there for the formation of the liquid ring already when starting the centrifugal pump 1 available.
  • the self-priming centrifugal pump 1 rests on feet 7 and has a cover 8, are housed under the drive and control means, with these drive and control means, the pumping action of the self-priming centrifugal pump 1 is controllable.
  • Fig. 2 the self-priming centrifugal pump 1 is shown in a longitudinal section.
  • a multi-part housing 9 houses the
  • the housing 9 is supported by a lantern 10, which connects to a motor 1 1 manufactures.
  • This engine 1 1 is typically designed as an electric motor and is controlled by an electronic control unit 12.
  • Engine 1 1 and control electronics 12 are arranged under the cover 8 and are supported by the feet 7.
  • the motor 1 1 has a motor shaft 13, with which a drive shaft 14 is releasably connected and rotationally fixed.
  • This drive shaft 14 carries a first impeller 15 and a second impeller 16.
  • the impellers 15 and 16 are by means of motor shaft 13 and
  • Drive shaft 14 mounted in a cantilevered manner and are rotatably supported by the bearings of the motor shaft 13.
  • the first impeller 15 is part of the normal-suction centrifugal pump 3 and has a first pumping section 17. This is arranged in a first chamber 18. Upon rotation of the drive shaft 14 fluid flows in the region of a rotation axis of Drive shaft 14 and thus of the first impeller 15 and is impacted from the first pump section 17 radially outward and there moved in the circumferential direction and pressurized.
  • the second impeller 16 is part of the liquid ring pumping stage 2 and comprises a second pumping portion 19. This second pumping portion 19 is disposed in a second chamber 20 and formed so that in this upon rotation of the
  • the detailed view A is shown enlarged in Fig. 3 and shows a section of the wheels and the region of the connection of both wheels together.
  • the drive shaft 14 passes through the housing 9 in the area in which housing 9 and lantern 10 are connected to each other.
  • the lantern 10 surrounds the
  • This mechanical seal comprises a rotating seal ring 21, which is arranged co-rotating with the drive shaft 14.
  • the rotating seal ring 21 is in sliding contact with a stationary seal ring 22 which is mounted in the housing 9 so as not to rotate with it.
  • a development of the mechanical seal is a flushed design according to DE 203 16 570 U1.
  • the first chamber 18 is separated from the second chamber 20 by a housing wall 23.
  • an opening 24 is provided, which is penetrated by a shaft portion 25.
  • the shaft portion 25 is made in this example as part of the second impeller 16 and includes a shaft end 26 and a constriction 27.
  • Shaft end 26 is in mechanical contact with the first impeller 15.
  • the transition point between the first impeller 15 and shaft portion 25 is sealed by means of a seal 28.
  • the seal 28 is designed as an O-ring, which is accommodated in an adapted contour such that no gap between it and the recording remains. This is advantageous for hygienic application, since deposits of dirt are prevented.
  • the shaft portion 25 is formed between the constriction 27 and the shaft end 26 tapered from the shaft end 26 to the constriction 27.
  • a diameter of the shaft portion 25 decreases from the transition to the first impeller 15 for constriction 27 out.
  • the constriction 27 causes together with the smooth course of a
  • the smooth course is given in the mathematical sense, if the intersection curve in Fig. 3 follows a curve with a steady slope. This means that kinks, steps or heels are avoided as far as technically feasible.
  • smooth is also given when the seal 28 has an exposed portion which interrupts the surface of the shaft portion 25 and the first impeller 15 and is exposed piecewise with a curvature. As long as a predominantly laminar flow along the surface of shaft portion 25 and the first impeller 15 remains educable, a sufficiently smooth course is given.
  • a further improvement of the flow path is given if, as in the example shown, an end face 29 of the second impeller merges with a groove 30 and thus with a smooth course in the shaft section 25. If the shaft portion 25 is made in one piece with the second impeller 16, the groove 30 is particularly simple and smooth to produce.
  • the shaft portion reaches in the constriction 27 its thinnest point
  • the constriction 27 may, as shown, have an extension in the longitudinal direction of the shaft portion.
  • the embodiment shows a connection of the drive shaft 14 with the first impeller 15 and the second impeller 16, which for receiving the flying from
  • the drive shaft 14 has at its end remote from the motor shaft 3 a truncated cone 31 which terminates in a cylindrical threaded portion 32. This threaded portion 32 is received in a thread in the shaft portion 25 under formation of a screw connection.
  • the first impeller 15 has a first clamping surface 33 which can be brought into mechanical contact with a second clamping surface 34 formed on the shaft section 25.
  • Screw connection with participation of the threaded portion 32 causes clamping forces which are introduced from the second impeller 16 via first clamping surface 33 and second clamping surface 34 in the first impeller 15 and cause a clamping on the truncated cone 32.
  • the second impeller has a base 35 to a cylinder.
  • On this at least one thread-like encircling blade 36 is provided. This blade 36 serves to create and maintain a liquid ring in the second chamber 20 and the screw-like passage of the gas phase through the second chamber 20. This at least one blade 36 forms the second
  • the blade At its end, the blade may have an extension 37 which projects beyond the end face 29 in the axial direction. This runs in the gap which exists between the end of the blade 36 and the housing wall 23 and there improves the formation of the liquid ring.
  • a perspective view of the second impeller 16 is shown in FIG. 4. The second
  • Impeller 16 in this figure has three blades 36 and each of the blades has at its end extensions 37 which are oriented in the axial direction.
  • Extensions 37 are provided on both the inlet 4 side facing as well as on the side of the shaft portion 25.
  • the cylinder 35 which is closed with an end plate 38, has an extract 39 arranged with Wrench surfaces with which the second impeller 16 can be screwed onto the threaded portion 32.

Landscapes

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

Abstract

L'invention concerne une pompe (1) auto-aspirante comprenant un boîtier (9), une entrée (4) et une sortie (5), une première roue mobile (15) pourvue d'un premier tronçon de pompe (17), qui est disposé dans un premier compartiment (18), et une deuxième roue mobile (16) pourvue d'un deuxième tronçon de pompe (19), qui est disposé dans un deuxième compartiment (20), et un tronçon d'arbre (25) prévu entre les tronçons de pompe (17, 19), lequel tronçon d'arbre (25) comprend une extrémité d'arbre (26) et traverse une ouverture (24) d'une paroi de boîtier (23). L'invention vise à améliorer le niveau de pression de maintien de la pompe (1). À cet effet, le tronçon d'arbre (25) situé entre un étranglement (27) et l'extrémité d'arbre (26) se déforme en se rétrécissant depuis l'extrémité d'arbre (26) en direction de l'étranglement (27). La première roue mobile (15) et le tronçon d'arbre (25) situé entre l'étranglement (27) et le premier tronçon de pompe (17) présentent un profil lisse.
EP16709450.7A 2015-03-13 2016-03-11 Pompe auto-amorçante Active EP3268616B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PL16709450T PL3268616T3 (pl) 2015-03-13 2016-03-11 Pompa samozasysająca

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102015003224.0A DE102015003224C5 (de) 2015-03-13 2015-03-13 Selbstansaugende Pumpe
PCT/EP2016/055283 WO2016146523A1 (fr) 2015-03-13 2016-03-11 Pompe auto-aspirante

Publications (2)

Publication Number Publication Date
EP3268616A1 true EP3268616A1 (fr) 2018-01-17
EP3268616B1 EP3268616B1 (fr) 2021-01-06

Family

ID=55524353

Family Applications (1)

Application Number Title Priority Date Filing Date
EP16709450.7A Active EP3268616B1 (fr) 2015-03-13 2016-03-11 Pompe auto-amorçante

Country Status (7)

Country Link
US (1) US10544795B2 (fr)
EP (1) EP3268616B1 (fr)
CN (1) CN107407283B (fr)
DE (1) DE102015003224C5 (fr)
ES (1) ES2860523T3 (fr)
PL (1) PL3268616T3 (fr)
WO (1) WO2016146523A1 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109026737A (zh) * 2018-08-02 2018-12-18 广州市能动机电设备有限公司 一种离心式水泵
IT201800020788A1 (it) 2018-12-21 2020-06-21 C S F Inox S P A Pompa centrifuga autoadescante
DE202020100267U1 (de) * 2020-01-20 2021-04-22 Evoguard Gmbh Selbstansaugende Pumpe und Vorrichtung
DE102020125805A1 (de) * 2020-10-02 2022-04-07 Frideco Ag Pumpensystem und Verfahren zum Betrieb eines Pumpensystems

Family Cites Families (21)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3082694A (en) * 1960-05-24 1963-03-26 Ingersoll Rand Co Self-priming centrifugal pump
NL6610840A (fr) * 1965-08-03 1967-02-06
DK395983D0 (da) * 1982-12-09 1983-08-31 Willy Johst Vaeskeringspumpe
US5599171A (en) * 1995-05-15 1997-02-04 Itt Fluid Technology Corporation Rotary, self-priming, liquip pump, and an impellers and shaft assembly therefor, and a flexible-impeller pump assembly
JP3924730B2 (ja) * 1996-07-26 2007-06-06 博 横田 自吸式遠心ポンプ装置
DE19918286A1 (de) 1999-04-22 2000-10-26 Ksb Ag Inducer
DK200000278U4 (da) 2000-09-20 2002-01-11 Apv Fluid Handling Horsens As Hygiejnisk selvansugende centrifugalpumpe.
KR100451651B1 (ko) * 2001-12-13 2004-10-08 엘지전자 주식회사 원심형 압축기의 역회전 방지구조
DE20316570U1 (de) 2002-11-02 2004-01-15 Tuchenhagen Gmbh Vorrichtung zur Spülung und/oder Kühlung einer Gleitringdichtungs-Einrichtung für eine Kreiselpumpe
WO2004058380A1 (fr) * 2002-12-26 2004-07-15 Kabushiki Kaisha Yokota Seisakusho Séparateur gaz-liquide
US7331770B2 (en) * 2003-01-14 2008-02-19 Oyaski Michael F Disposable two-stage pump
US7287963B2 (en) * 2003-09-30 2007-10-30 Dimension One Spas Fast pump priming
DE202004013752U1 (de) 2004-09-03 2004-12-02 Tuchenhagen Gmbh Vorsatzlaufrad für eine Kreiselpumpe
DE102007032228B4 (de) 2007-07-11 2016-01-07 Gea Tuchenhagen Gmbh Selbstansaugende Pumpenaggregation
US8998586B2 (en) * 2009-08-24 2015-04-07 David Muhs Self priming pump assembly with a direct drive vacuum pump
DE102011106525A1 (de) * 2011-07-04 2013-01-10 Gea Tuchenhagen Gmbh Dispergierpumpe
US9587641B2 (en) * 2012-04-11 2017-03-07 Waterous Company Integrated reciprocating primer drive arrangement
US20130320148A1 (en) * 2012-06-05 2013-12-05 Honeywell International Inc. Impeller, centrifugal pump including the same, and aircraft fuel system including the centrifugal pump
EP2894343B2 (fr) * 2014-01-12 2021-09-01 Alfa Laval Corporate AB Pompe centrifuge à amorçage automatique
DK2894342T3 (en) * 2014-01-12 2017-04-03 Alfa Laval Corp Ab SELF-TILTING CENTRIFUGAL PUMP
CN204082563U (zh) * 2014-08-08 2015-01-07 陕西航天动力高科技股份有限公司 一种高抗汽蚀快速自吸油泵组

Also Published As

Publication number Publication date
CN107407283B (zh) 2019-09-03
US10544795B2 (en) 2020-01-28
US20180058466A1 (en) 2018-03-01
ES2860523T3 (es) 2021-10-05
CN107407283A (zh) 2017-11-28
EP3268616B1 (fr) 2021-01-06
DE102015003224C5 (de) 2021-07-15
PL3268616T3 (pl) 2021-08-09
WO2016146523A1 (fr) 2016-09-22
DE102015003224B4 (de) 2018-02-08
DE102015003224A1 (de) 2016-09-15

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