EP0038389A1 - Pompe pour le transfert de matières solides - Google Patents

Pompe pour le transfert de matières solides Download PDF

Info

Publication number
EP0038389A1
EP0038389A1 EP80301254A EP80301254A EP0038389A1 EP 0038389 A1 EP0038389 A1 EP 0038389A1 EP 80301254 A EP80301254 A EP 80301254A EP 80301254 A EP80301254 A EP 80301254A EP 0038389 A1 EP0038389 A1 EP 0038389A1
Authority
EP
European Patent Office
Prior art keywords
impeller
pump
circular
sections
section
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP80301254A
Other languages
German (de)
English (en)
Inventor
Michael Leslie Ryall
John Mcfarlane Taylor
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.)
Weir Pumps Ltd
Original Assignee
Weir Pumps Ltd
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 Weir Pumps Ltd filed Critical Weir Pumps Ltd
Priority to EP80301254A priority Critical patent/EP0038389A1/fr
Publication of EP0038389A1 publication Critical patent/EP0038389A1/fr
Withdrawn legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D1/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D1/14—Pumps raising fluids by centrifugal force within a conical rotary bowl with vertical axis

Definitions

  • This invention relates to pumps for low head duties of the general type described in UK Patent No.1464762, in which a spiralling liquid vortex with an air core is created inside a vertical rotating impeller wall; the lower end of this impeller being below the liquid surface of the reservoir or sump from which it draws suction- the impeller serving to lift the liquid by "centrifugal”action from this sump to a higher level through the formation of the aforementioned spiralling vortex.
  • vanes generally of spiral form, attached to the inside surface of the rotor outer wall, and extending from or near the bottom of the rotor to a level at or near, but not generally above, the top of the rotor.
  • vanes have generally, but not necessarily, been attached to a central driving shaft, through which torque has been applied to the impeller.
  • the object of the present invention is to overcome these solids handling limitations.
  • a cone or barrel pump comprises .a hollow impeller rotatable about an axis and having an internal annular working surface, said internal annular working surface having cross-sections of non-circular form whereby said working surface creates a pumping effect on rotation of the impeller.
  • the impeller need not carry vanes.
  • the previous barrel . pump comprising an outer containment shroud of a substantially circular cross-section symmetrically disposed about the drive shaft, and spirally mounted driving vanes connecting this shroud with the drive shaft is replaced by a pump having an impellor with an internal cross-sectional form defining internal lobe means with preferably two or more lobes disposed about the impeller vertical axis.
  • This 'lobed' rotor is not fitted with internal vanes to impart the torque directly to the spiralling vortex, but imparts the torque to this vortex by virtue of variations in pressure which will occur on the inner working surface of the lobe walls.
  • the wall of the impeller carries two longitudinal upstanding formations.
  • a greater number of upstanding formations may be used provided that the symmetry of cross section throughout the length of the impeller about the vertical axis is maintained.
  • the changing radial length of the working surface of the impeller at transverse sections due to the provision of the upstanding formations, has the effect of providing the impeller with internal "lobes".
  • the upstanding formations may be of straight longitudinal form or alternatively may be helically arranged.
  • the cross-section of the non-circular working surface may be of approximate rectangular form, but with two facing concavely curved ends.
  • the upstanding formations can be such as to provide the cross section with two facing pairs of curved portions, one concave the other convex whereby the lobed arrangement is emphasised.
  • the impeller has an intermediate working portion of non-circular (lobed) form blending into circular cross-sectioned mouth and discharge portions at either end of the intermediate portion.
  • transition from a symmetrically disposed circular cross section impeller inlet at its lower extremity to a lobed cross section is progressive and not sudden, so that all surfaces, with which the spiralling vortex makes contact during its progression up the impeller, present smoothly varying profiles to the flow with no sudden discontinuities. It is also a preferred feature of this invention that there is a smooth transition from a 'lobed' section of the impeller, over its 'pumping' length to a symmetrically disposed circular section at its outlet, to effect even discharge of liquid from the rotor around its periphery at outlet.
  • the discharge portion may discharge into a reservoir via a bell-mouth or a diffuser could be provided intermediate the impeller and the reservoir, and the impeller mouth or inlet may also be of bell-mouth form and so arranged that liquid can enter the pump without substantial obstructions.
  • the impeller is axially supported by means of a shaft having an end connected to the upstanding formations, and an external rotary bearing may be provided engaging the external wall of the impeller for radial support thereof.
  • the impeller may be driven by a drive to the impeller's external wall.
  • bearing means are provided engaging the outer wall of the impeller for both axial and radial support of the impeller.
  • the impeller may be made of glass fibre reinforced plastics material, with the longitudinal formations bonded to the impeller wall.
  • driving vanes or spokes 7 are introduced internally to permit the impeller rotor 2 to be mounted on a central drive shaft 8. These vanes 7 are disposed so that they provide no real obstruction to the flow of the rotor 2, such flow being in the form of a vortex flow 9 and confined to the channels up the rotor 2, defined by the lobes 4 by the time the flow has reached Section VII, i.e. the free surface 10 of the vortex is radially outwith the vanes 7.
  • Sections VII and X the lobes progressively change to a circular cross section at Section X (Fig. 7) which in this example is the upper limit of the pumping (or torque input) portion of the rotor 2.
  • the portion of the rotor 2 between Sections X and XIV (Fig. 8) is a simple coned section of upwardly diverging form.
  • the lobe sections between Section 0 and Section X may either be disposed axially in line with each other as shown in Fig. 1 or (preferably) may be angularly displaced or 'screwed round' relative to each other as in Figs.14 and 15 in any prescribed form to induce efficient flow of liquid axially and radially outward into the lobes 4, and up the lobe channels.
  • the external surface of the impeller rotor 2 is circular at all sections 0 to XIV, the diameter at each section being that required to circumscribe the lobed or circular internal cross section ( as shown in Figs. 2 to 8).
  • the rotor 2 as described is mounted vertically with its bellmouth 3 below the surface of the suction sump Rl from which it draws.
  • liquid is drawn through the bellmouth 3 into the impeller and flows upwards and radially outwards into the lobes 4, where whirl is progressively imparted to the liquid.
  • This whirl causes the liquid to flow up the internal channels in the rotor shroud formed by the lobes 4, and a free surface 10 is formed on the inner diameter of the liquid vortex 9.
  • the design of the impeller rotor lobes, the rotational speed, and the immersion depth of the bottom of the rotor in the suction sumps are all arranged so that by the time the liquid has risen up the rotor to Section VII, as a result of the whirl applied to it, it is fully confined to the lobe channels, with an internal free surface; and the support and drive vanes or ribs mounted between Sections VII and X to connect the rotor to the vertical drive shaft above it do not therefore interfere with the lobe channel flow in any way. Whirl imparted to the liquid vortex is progressively increased up to section X.
  • the liquid then flows into the conical diffusing part of the rotor between Sections X and XIV, in which some of its velocity energy is converted to potential energy. From Section XIV, the liquid is then discharged into a rotating (not shown) or stationary diffusing section 15 ( as shown) in which further recovery of potential energy from velocity energy is effected.
  • the impeller rotor is mounted on, and driven by, a vertical drive shaft 8 by vanes 7,radial location being also provided at a lower position, preferably above the liquid surface, by three or more rollers 11 engaging a ring 12 which forms part of the rotor shroud and is able to rotate
  • the impeller rotor 2 is radially and axially restrained entirely by rollers 11 in contact with two or more rings 12 attached to the outer shroud, and the drive shaft and vanes can be eliminated.
  • input torque to the rotor is preferably provided by a toothed belt 13 or chain drive from a prime mover or motor 14 mounted alongside the impeller 2, the belt 13 drivingly engaging a ring ( e.g. ring 12 bn the impeller 2.
  • two lobes are used in the impeller cross section. These lobes may be of any cross section ' form consistent with ease of manufacture, smooth internal surfaces, and good liquid entrainment capacity. Any number of lobes may be chosen but in .general two or three lobes have been found to be the most suitable. Instead of a general rectangular cross section (as shown in Figs. 2 to 8), a cross section comprising facing pairs of concave and convex curves could well be used, to give more pronounced lobe portions 4. Figs 10 to 12 illustrate such alternative cross sections and these can be achieved by suitability shaping the formations 6 on the impeller internal wall.
  • the impeller 2 with internal wall formations 6 could be of glass reinforced plastics material with the formations 6 formed integral with or bonded to the impeller outer circular wall, or the impeller could be formed by castings.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
EP80301254A 1980-04-18 1980-04-18 Pompe pour le transfert de matières solides Withdrawn EP0038389A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP80301254A EP0038389A1 (fr) 1980-04-18 1980-04-18 Pompe pour le transfert de matières solides

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP80301254A EP0038389A1 (fr) 1980-04-18 1980-04-18 Pompe pour le transfert de matières solides

Publications (1)

Publication Number Publication Date
EP0038389A1 true EP0038389A1 (fr) 1981-10-28

Family

ID=8187148

Family Applications (1)

Application Number Title Priority Date Filing Date
EP80301254A Withdrawn EP0038389A1 (fr) 1980-04-18 1980-04-18 Pompe pour le transfert de matières solides

Country Status (1)

Country Link
EP (1) EP0038389A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3519284A1 (de) * 1985-05-30 1987-01-02 Ruppert Hans Dipl Ing Pumpanlage

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB117326A (en) * 1917-08-07 1918-07-18 Henri Arnold Johanne Nachenius Improvements in and relating to Centrifugal Pumps.
US1361938A (en) * 1918-12-23 1920-12-14 Nelson B Waldron Centrifugal pump
DE712738C (de) * 1937-05-14 1941-10-24 Aeg Motortauchpumpe mit einem Aussenlaeufermotor
US3075459A (en) * 1960-06-17 1963-01-29 Dow Chemical Co Centrifugal pump
US3504990A (en) * 1967-05-09 1970-04-07 David B Sugden Undulating flow promoting rotor and assemblies embodying same
DE2157743A1 (de) * 1970-11-23 1972-06-29 Tait Mfg Co The Schaufelloses Pumpenlaufrad
US3809491A (en) * 1973-07-05 1974-05-07 A Banyai Centrifugal pump structure

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB117326A (en) * 1917-08-07 1918-07-18 Henri Arnold Johanne Nachenius Improvements in and relating to Centrifugal Pumps.
US1361938A (en) * 1918-12-23 1920-12-14 Nelson B Waldron Centrifugal pump
DE712738C (de) * 1937-05-14 1941-10-24 Aeg Motortauchpumpe mit einem Aussenlaeufermotor
US3075459A (en) * 1960-06-17 1963-01-29 Dow Chemical Co Centrifugal pump
US3504990A (en) * 1967-05-09 1970-04-07 David B Sugden Undulating flow promoting rotor and assemblies embodying same
DE2157743A1 (de) * 1970-11-23 1972-06-29 Tait Mfg Co The Schaufelloses Pumpenlaufrad
US3809491A (en) * 1973-07-05 1974-05-07 A Banyai Centrifugal pump structure

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3519284A1 (de) * 1985-05-30 1987-01-02 Ruppert Hans Dipl Ing Pumpanlage

Similar Documents

Publication Publication Date Title
US4063849A (en) Non-clogging, centrifugal, coaxial discharge pump
US4143999A (en) Fluid machines
CA2856861C (fr) Dispositif d'orientation de debit pour l'acheminement d'un materiau a un rotor
US7896617B1 (en) High flow/high efficiency centrifugal pump having a turbine impeller for liquid applications including molten metal
US3771900A (en) Graduated screw pump
US7766605B2 (en) Centrifugal pump
KR930008352B1 (ko) 와류 펌프
US20030196952A1 (en) Sand and particle separator for fluid pumping systems
EP0216969A1 (fr) Pompe centrifugue
CN214366878U (zh) 用于离心泵的叶轮
EP0038389A1 (fr) Pompe pour le transfert de matières solides
GB2046359A (en) Centrifugal pumps
US4318670A (en) Screw pump for conveying waste water and the like
DE2514970A1 (de) Rotodynamische fluidmaschine
JPS5920878B2 (ja) バレル・ポンプ
US2921532A (en) Submerged motor pump
US4228948A (en) Centrifugal liquid cleaner
US4531887A (en) Continuous blade multi-stage pump
EP3642490A1 (fr) Hélice hélicoïdale
RU2132973C1 (ru) Центробежное реактивное рабочее колесо
CN2185817Y (zh) 涡流泵
US20240141915A1 (en) Pump comprising an impeller body provided as an oblique cone
US10883508B2 (en) Eddy pump
SU1760170A1 (ru) Насосна установка
US2284632A (en) Centrifugal pump

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Designated state(s): DE FR NL SE

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

Free format text: STATUS: THE APPLICATION HAS BEEN WITHDRAWN

17P Request for examination filed

Effective date: 19820422

18W Application withdrawn

Withdrawal date: 19820513

RIN1 Information on inventor provided before grant (corrected)

Inventor name: TAYLOR, JOHN MCFARLANE

Inventor name: RYALL, MICHAEL LESLIE