[go: up one dir, main page]

US2641191A - Guide means on impeller for centrifugal pumps or blowers - Google Patents

Guide means on impeller for centrifugal pumps or blowers Download PDF

Info

Publication number
US2641191A
US2641191A US786605A US78660547A US2641191A US 2641191 A US2641191 A US 2641191A US 786605 A US786605 A US 786605A US 78660547 A US78660547 A US 78660547A US 2641191 A US2641191 A US 2641191A
Authority
US
United States
Prior art keywords
impeller
vanes
annular
inlet
pressure medium
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.)
Expired - Lifetime
Application number
US786605A
Other languages
English (en)
Inventor
Buchi Alfred
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.)
Individual
Original Assignee
Individual
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 Individual filed Critical Individual
Application granted granted Critical
Publication of US2641191A publication Critical patent/US2641191A/en
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/44—Fluid-guiding means, e.g. diffusers
    • 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
    • F04D29/2272—Rotors specially for centrifugal pumps with special measures for influencing flow or boundary layer
    • 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
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/44—Fluid-guiding means, e.g. diffusers
    • F04D29/445—Fluid-guiding means, e.g. diffusers especially adapted for liquid pumps

Definitions

  • BUCHI June 9, 1953 GUIDE MEANS ON IMPELLER FOR CENTRIFUGAL PUMPS 0R BLOWERS Filed NOV.
  • the invention relates to a special embodiment of the inlet device on impellers for single-stage or multi-stage centrifugal pumps or blowers.
  • at least one funnelshaped annular vane is arranged into the intake throat of the impeller which guides the pressure medium from the axial to the radial direction, so that said annular vane, together with the confining surfaces of the intake throat, guides the pressure medium from the axial to the radial flow direction.
  • the object of the invention may be so chosen and dimensioned that the funnel-shaped annular vane or vanes are fastened in the static section of the inlet casing, surrounding the impeller inlet, and the actual impeller blading starts only beyond the approximately radial exit of the annular vane or vanes.
  • annular vane or vanes may also be built into the centrifugally-acting impeller blading proper, extending inwardly towards the inlet throat for the pressure medium.
  • additional vanes may be built into the entrance section of the impeller, e. g. vanes which impart a radial flow direction to the entering pressure medium, ahead of the centrifugally-acting impeller blades. If the embodiment is such that the annular vanes are to rotate with the impeller and the additional vanes are fixed in the static casing, then the additional vanes have to be slotted.
  • the object of the invention can also be so arranged that in case of impellers with impeller blade tips extended axially towards the entrance throat for the pressure medium, the annular vane or vanes are built at least into the impeller section which guides the pressure medium from axial to radial direction.
  • the annular vanes may extend, in this case, up to the inner ends of the impeller blades, or they may be shorter be so formed that the radii of curvature Of the passages created between the impeller walls and the annular vane or vanes, vary from the inlet in the direction of the pressur medium flow, i, e. they decrease or increase.
  • the impeller walls, as well as the built-in annular vane or vanes, may on one hand be so dimensioned and shaped that the Velocity of the pressure medium increases from the entrance towards the radial section of the impeller, and that on the other hand, in the same section, the radii of curvature of the passages which are created between the Walls of the impeller and the annular vane or vanes, vary in the direction of the pressure medium flow, so, that despite the necessary curvature of said passages into radial direction there will be no substantial flow detachment of the pressure medium from the walls.
  • the annular vane or vanes may be divided (i. e. made in several parts) in at least one plane thrOugh the blower axis.
  • the static annular vane or vanes may be cast Or welded into the static entrance section of the pump or blower.
  • the rotating type of annular vane 01' vanes may also be cast or welded into the impeller blading.
  • the arrangement with axially protruding impeller blade ends and with annular vane or vanes extending into the impeller blading may also be made so that the thus formed passages for the pressure medium in the impeller have approximately square cross section, to keep the losses in these passages to a minimum.
  • a sufficient number of annular vanes may be built in, that the thus determined radii of curvature of the passages between the confining walls of the impeller and the walls of the built-in funnelshaped annular vanes are at least greater than the width of the corresponding, curved passages for the pressure medium.
  • the annular vanes may, however, also be made curved and built-in so that the radii of curvature, in relation to the width of the passages for the pressure medium created between the impeller walls and the annular vanes, ar approximately equal for all pafisages.
  • At least two annular vanes may be built into the intake means of the impeller.
  • the passages confined between the impeller walls and the annular vanes can be made to have relatively large radii of curvature-e. g. of twice or more times the passage Width--whereby the flow deflection losses are reduced.
  • the arrangement is made preferably so that the ratio of radius of curvature to width of passage is approximately equal for all passages.
  • the number of the impeller blade ends and of the annular vanes may be chosen s0-for the sake of reduction of losses-that the thus created passages have approximately square cross section.
  • the intake means may also contain a sufficient number of annular vanes so formed and dimensioned that in all the inlet ducts thus created the sum total of all losses through friction, flow defiection and energy transition in the various separate entrance passages up to the proper centrifugally-acting impeller blading will be about equal and/or will be a minimum.
  • At least one annular vane deflecting the pressure medium by approximately 180 degrees may be built in.
  • annular vanes there may also be arranged a sufficient number of annular vanes in at least one of the two guideand impeller-sections equipped with such annular vanes, and the vanes be so shaped and located, that the velocity and pressure conditions over the whole admission area for the pressure medium leading to the centrifugally-acting impeller blading will be at least approximately equal.
  • the built-in annular vanes may also be of divided construction.
  • the built-in annular vanes may be arranged on constructed in such numbers, shapes and with such radii of curvature that there will be minimum flow losses in the thus created guide passages and/or all losses in these guide passages being about equal.
  • Special impellers with axially-acting blading may be arranged ahead of the centrifugally-acting impellers, whereby the former guide the pressure medium to the latter with a minimum of shock losses. Also, at least one axially-acting impeller may be arranged ahead of the centrifugally-acting impeller so that it transmits the pressure medium to the latter via a guide wheel. In this case, too, the inlet section of the blading of the centrifugally-acting impeller is to be shaped accordingly.
  • the object of the invention is illustrated in the enclosed figures in several examples of centrifugal blowers. Same numbers or letters mean same or similar parts.
  • the application of the invention on centrifugal pumps can easily be deducted therefrom, since those machines contain similar parts.
  • FIGs. 1 and 2 show sections through singlestage centrifugal. blowers wherein the invention is embodied in the simplest form.
  • Fig. 3 illustrates a section through a shrouded impeller of a single-stage blower, whereby the object of the invention is applied in a different form on an impeller with backward-curved vanes.
  • Fig. 9 illustrates a section through a still further embodiment of the invention.
  • Fig, 10 is an axial view of the corresponding inlet device after it is removed outside of the impeller, viewed in a direction opposite to the pressure medium flow.
  • Figs. 11 and 12 show possible forms and arrangements of annular vanes built into the inlet opening of the impeller; Fig. 11 shows an open impeller with vanes extended as far as the inlet opening of the impeller, and Fig. 12 shows a shrouded impeller.
  • Figs. 13 and 14 show vertical sections through the axis of multi-stage centrifugal blowers.
  • the casing of this blower is divided lengthwise (in axial direction) into two parts.
  • Fig. 14 shows a multi-stage blower where the casing parts and the impellers are designed to be assembled axially and successively, so that the casing joints are vertical.
  • I is the impeller of the centrifugal blower, keyed upon shaft 2.
  • the impeller I has centrifugal vanes 3 and a shroud 4.
  • the twopiece blower casing 5 and 6 encloses the impeller I and has a joint 1.
  • the pressure medium enters the casing at 8 and is led into the blower casing 9; from there it is fed through pressure tube III to its destination.
  • the object of the invention is the annular vane l I, which juts into the inlet section I2 of the impeller I and aids the flow deflection of the pressure medium in thi section from the predominantly axial direction to the at least approximately radial direction of the centrifugal impeller vanes 3.
  • the onepiece annular vane II is cast into the ribs I3 of the blower casing which connect the fixed central section I4 with the blower volute 9.
  • the inner diameter I5 of the annular vane II is just large enough to avoid touching the inner edges I8 of the impeller vanes 3 by said annular vane I I, and to permit detachment of easing part 5, with the thereto-attached annular vane II, from casing part 6 without blocking by the inlet edge I I of the impeller shroud 4.
  • the annular vane I I is arranged relatively closely to impeller shroud 4.
  • the impeller I has vanes 3 but no shroud, so that casing part 5 laterally encloses the vanes 3 with small clearance.
  • the impeller vanes 3 are extended axially towards the inlet of the impeller and terminate in the approximately radially-arranged inlet edges [8.
  • An annular vane II is so arranged that it is set back some distance from the impeller vane inlet edges I6, and that it provides the flow deflection of the pressure medium from axial to radial direction.
  • This annular vane II may be cast into impeller blades 3, or fixed therein in some other manner. It is arranged, as seen from the figure, more closely towards the outer side of the impeller vanes. This is done to avoid serious discrepancies in the ratios between radius of curvature and passage width, and the consequent discrepancies in losses.
  • I is the impeller with shroud 4 and impeller vanes 3.
  • the latter terminate inwardly at the edges I6.
  • two annular vanes I I and II are built-in; their outer ends are cast into the impeller vanes 3.
  • an embodiment according to Fig. 3 has backward-curved impeller vanes 35.
  • the annular vanes II and II are so located that three annular passages It, I8 and I8" are created between the confining walls of the impeller and the two annular vanes.
  • These annular passages have different widths, so that passage it is narrowest, and passage I8" is wid st.
  • the mean radii of curvature of the three passages can be made to have approximately eoual ratio to the widths of the corresponding ducts.
  • the deflection losses in the three annular passages can therefore be kept about equal, so that ap proximately equal pressure and velocity conditions will prevail over the whole cross section at the exit of said annular passages towards the con trifugally-acting section of the impeller.
  • Figs. 5 and 6 show an open centrifugal blower im eller I in which the impeller blades 3 are radially arranged on their centrifugal part, and axially so extended at 3 and bent around at their inlet edges Iii that they admit the axially-inrusl1- ing pressure medium approximately shock-free.
  • Two annular van s II and. II are also arranged here in the impeller blading section towards the pressure medium entrance. They may be cast-in or weldeddn, for example.
  • the inner part of the impeller hlading with the ax ally extended inlet edges l5 and with the annular vanes II and i! may, on the other hand, also be bui t as a part containing the inner passa es it and It".
  • the outer of vanes may be held in a ring 2
  • Such a vane part is illustrated a section in '7 and in axial view in 8.
  • the inner part of the im peller is separated from the centrifugal impeller proper.
  • This piece may be fastened at the hub section of impeller I, e. g. by means of ring it. It is built in at 3" inside of th outwardly-located impeller vanes 3. Between the ring 29 and easing part 5, seals 2i may be arranged.
  • Ring 2b may be seated, as shown on Fig. 7, directly upon the vanes 3 of an open impeller, or it may be fastened there.
  • the vanes 55" abutting against impeller disc I may also have axially-directed protrusions 26 which may reach e. g. into the impeller disc I, or they may he riveted or welded, etc. thereon.
  • the inset blading section may also be so shaped that it reaches up to the inclined edges 3a" of the impeller vanes 3.
  • FIGs. 9 and 10 an embodiment similar to the one in Fig. l is shown.
  • the annular vane II is also here fastened in the ribs I3 of the blower casing 3.
  • eight thin, radial vanes 22 are also fastened in the ribs I3.
  • These annular vanes, together with the eight radial vanes 22 and with the confining walls of impeller I and shroud enclose sixteen radially-curved guide passages for the pressure mg 3 can be maintained.
  • the ribs 22, aswell as the annular vane II may be cast, welded, or soldered, etc, into the ribs I3;
  • Figs. 11 and 12 illustrate, on two construction examples, the variety of shapes that can be given to the annular vanes and impeller walls at their inlet ends.
  • Fig. 11 shows an open impeller I. It is equipped with vanes 3 which extend axially up to edge I6. 5 is the casing part which encloses or covers the impeller 'blading on the outside.
  • the annular vanes I I and I I located in the inlet section of the impeller blading, show sharper curvature at the inlet ends, and reduced curvature towards the radial part of the impeller.
  • the widths of the ducts created between the confining walls of the impeller and the annular vanes II and l I are larger at the pressure medium intake b1, b2, in than at the exit -b1, bz, b':;.
  • the annular vanes II and I I are unevenly placed so that the ratio of the mean radii of curvature r1, r2, 1'3 of the passages to the mean passage widths b1, b2, be is at least approximately larger than unity at the entrance, and increases to still higher values toward the exit bi, b'a and 13's.
  • annular vanes I I and I I may be of diiierent length on their intake or on their exit, as visible in Fig. 11.
  • Fig. 12 shows annular vanes so shaped that at the inlet ends they have relatively large, though uneven, radii of curvature 11,12, 'rs compared to the passage widths b1, b2, b3, and have relatively small radii of curvature r'i, 7"2, 7"3, compared with the passage widths b'i, bz, b'3 at the exit ends.
  • the passage widths b1, b2, b3 and bi, bz, b's, respectively, are chosen uneven, too. They are largerat the pressure medium inlet than at its exit, so that an accelerated flow through the passages is achieved.
  • the inner ends I51 and IP52 of the annular vanes II and i I are so dimensioned that they do not touch the impeller'vanes 3 and I 6, but still provide most complete flow deflection to radial direction.
  • the ratio of radius'of curvature to passage width is large at the pressure medium intake, and smaller at the rear end'of the annular vanes II and II.
  • the ratio of radius of curvature to width of the guide passages can be made much larger than in case of no such annular vanes.
  • the losses through flow deflection of the pressure medium from axial to radial direction can be greatly reduced.
  • the intake flow losses to "the impeller can be reduced to a minimum, and/or the intake velocities to the centrifugal impeller blading, measured over the whole intake cross section, can be made equal, at equal'pressure.
  • Fig. 13 shows a section through the axis of a multi-stage centrifugal blower. It contains three impellers lb, lb, and lb arranged in series; The pressure medium enters at A and is discharged at B. All the three impellers lb, lb, and lb are keyed upon shaft 2, which is driven through coupling flange 2.
  • the casing 9', 9" which encloses all the impellers, is divided into two sections at the horizontal plane 9".
  • the object of the invention is incorporated in impeller la in similar manner as in the embodiment shown in Fig. 3.
  • Two annular vanes a and I I'll are built into the impeller vanes 3b. They terminate at His about parallel to the blower axis, however.
  • the impellers In, and lb discharge the pressure medium first to one guide device each, 23 and 24, where velocity is converted to pressure. Then the pressure medium is led through receivers 25 and 26, respectively, to the passages 27 and 28 which guide it radially inward again.
  • the latter are equipped with vanes 30a and 39b which impose a predominantly radial flow direction to the pressure medium, particularly near the blower shaft.
  • the pressure medium is led axially towards the inlet of the adjacent impeller lb or '0, respectively, by means of the casin walls which are curved, near the axis, from radial to axial direction.
  • the flow deflection from space 21 into the impeller interior lb which amounts to nearly 180 angular degrees, can be aided greatly by an embodiment of this invention.
  • Fig. 13 it consists in at least one annular vane each (21', 21 and 28', respectively) built into the exits of the transmitting pieces 21 and 28. They guide, together with the rounded confinin walls of the guide parts 21 and 28, respectively, the pressure medium to the inlet of the adjacent impellers lb and '0, respectively, with a possible minimum of losses through deflection, friction, etc. Additional annular vanes llb, llb and c of a type hereinabove described are built into the impeller inlets.
  • the annular vanes 21', 21" and 28, respectively, are preferably so shaped and arranged in relation to the annular vanes l l, l lb and l '0 in the impellers lb and Is, that the full deflection of the pressure medium from radially-inward direction via axial to radially-outward direction is accomplished with minimum velocity and pressure losses, and/or with even velocity and pressure distribution of the pressure medium over the whole inlet cross section of the centrifugally-acting impeller blading.
  • Fig. 14 illustrates also a section through a threestage blower with impellers lb, lb, lb.
  • the blower casing consists here of four disc-shaped parts 9'1, 9'2, 9'3 and 9'4 which may be separated from each other along radially-extended joints 291, 292 and 293 upon loosening of the corresponding flange connections. Assembly of the blower is accomplished by first mounting the blower part 9'4 on the shaft 2 from the left-hand side, then sliding the balancing piston 39 on the shaft from the right-hand side, followed by impeller lo, and then fastening the blower casing part 9'3 on casing part 9'4. Thereupon the impeller lb, casing part 9'2, impeller lb, and, last, the inlet casing part 9'1 are assembled in that order.
  • deflecting vanes I la and l l 'a are built into the inlet section of the blading 3b of impeller lb.
  • the annular vanes II- and llb are built into impeller la. similarly as illustrated already in Fig. 3.
  • Annular vanes l lb and l l'b are arranged in the intake section of impeller lb, and an annular vane c is installed in the inlet of impeller '0.
  • Installation of the annular vanes l lb and llb and I '0, respectively, is done by insertion or by casting-in into vanes 30b and 30b, respectively, which subdivide the guide passages 21 and 28.
  • These annular vanes are thus rigidly connected to the casing parts 9'2 and 9'3, and extend into the inlet sections of the impellers lb and l c, close to the inner impeller blade edges lBb and Ne.
  • the outer diameters l5b, l5'b and We of the annular vanes llb, llb and He, respectively, are chosen just large enough that the casing parts 9'2 and 9'3 can be readily withdrawn axially from the impeller inlet openings.
  • the shape, radii of curvature, and position of the annular vanes can be so chosen that minimum velocity and pressure losses will occur in the deflecting passages between the guide passage sections 21 and 28, respectively, and the impeller'inlet lb and '0, respectively.
  • the annular vanes may also be arranged in such numbers, shapes, and positions, that the inlet conditions will be approximately equal over the whole inlet cross sections of impeller blades 3b and 3c.
  • the invention provides improved inlet conditions on centrifugally-acting impellers.
  • the pressure medium has to be deflected by about degrees from axial to radial direction in case of single-stage blowers or pumps or on the first stages of multi-stage blowers or pumps.
  • the deflection amounts to nearly degrees in case of the subsequent stages of multi-stage blowers or pumps.
  • This sharp deflection causes losses through deflection, friction, andif the passage areas are variable-also throughv energy transition.
  • These losses, or their sum total are to be reduced by the insertion of the proposed annular vanes.
  • the latter may be so shaped and located that throughout the whole inlet section for the pressure medium to the centrifugallyacting impeller blades there will prevail approximately equal velocity and pressure conditions.
  • the number and design of the annular vanes should be so chosen that the ratio of curvature radius to width of passage, for the passages so formed, will be as large as possible. This ratio is to be chosen differently for the individual guide passages so that the sum total of all losses therein is equal and/or is a minimum.
  • a centrifugal p mp or blower having an axial inlet eye and a blade supporting wheel, impeller blading on said wheel, a casing about said wheel and said blading, said casing having an annular portion defining the outer perimeter of said eye, said wheel having a portion beginning near the center of said eye, extending axially inwardly and curving from axial to radial direction to define with the inner portion of said casing a curved annular passage subdivided by said blading whereby the fluid to be pumped or blown is admitted axially through said eye and is forced centrifugally radially outwardly of said blower wheel, and funnel shaped annular vane means disposed in said passage beginning at least within said eye and curving with the blower wheel portion and inner portion of said casing defining said passage to subdivide said passage into a plurality of smaller annular passages, said vane means being of such progressive diameters that the resulting ratios of the mean radii of curvature to the mean widths

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
US786605A 1946-11-12 1947-11-18 Guide means on impeller for centrifugal pumps or blowers Expired - Lifetime US2641191A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CH2641191X 1946-11-12

Publications (1)

Publication Number Publication Date
US2641191A true US2641191A (en) 1953-06-09

Family

ID=4570726

Family Applications (1)

Application Number Title Priority Date Filing Date
US786605A Expired - Lifetime US2641191A (en) 1946-11-12 1947-11-18 Guide means on impeller for centrifugal pumps or blowers

Country Status (2)

Country Link
US (1) US2641191A (ru)
BE (1) BE477688A (ru)

Cited By (24)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2809493A (en) * 1951-03-19 1957-10-15 American Mach & Foundry Centrifugal flow compressor and gas turbine power plant with a centrifugal flow compressor, toroidal combustion chamber, and centripetal flow turbine
US3058650A (en) * 1955-05-05 1962-10-16 American Radiator & Standard Air conditioner
US3095821A (en) * 1960-05-02 1963-07-02 Elenbaas Herman Sanitary centrifugal pump
US3165257A (en) * 1962-10-03 1965-01-12 Howard C Edwards Pressure inducer
US3289922A (en) * 1964-10-30 1966-12-06 Utah Construction & Mining Co Air compressor
US3365122A (en) * 1966-02-02 1968-01-23 Rotron Mfg Co Centrifugal blower
US4865519A (en) * 1988-02-12 1989-09-12 Institut Of Engineering Thermophysics Of Chinese Academy Of Sciences Oil submersible pump
US5362203A (en) * 1993-11-01 1994-11-08 Lamson Corporation Multiple stage centrifugal compressor
US20090208331A1 (en) * 2008-02-20 2009-08-20 Haley Paul F Centrifugal compressor assembly and method
US20120121399A1 (en) * 2009-07-31 2012-05-17 Rem Enterprises Inc. air vacuum pump for a particulate loader and transfer apparatus
WO2014090559A2 (de) * 2012-12-14 2014-06-19 Sulzer Pumpen Ag Pumpvorrichtung mit einem strömungsleitelement
CN104791254A (zh) * 2015-04-22 2015-07-22 大连深蓝泵业有限公司 大功率轴向剖分双吸两级泵
US10876545B2 (en) * 2018-04-09 2020-12-29 Vornado Air, Llc System and apparatus for providing a directed air flow
US10941778B2 (en) 2018-08-16 2021-03-09 Saudi Arabian Oil Company Motorized pump
US11371326B2 (en) 2020-06-01 2022-06-28 Saudi Arabian Oil Company Downhole pump with switched reluctance motor
US11499563B2 (en) 2020-08-24 2022-11-15 Saudi Arabian Oil Company Self-balancing thrust disk
US11591899B2 (en) 2021-04-05 2023-02-28 Saudi Arabian Oil Company Wellbore density meter using a rotor and diffuser
US11644351B2 (en) 2021-03-19 2023-05-09 Saudi Arabian Oil Company Multiphase flow and salinity meter with dual opposite handed helical resonators
US11767741B2 (en) 2018-08-16 2023-09-26 Saudi Arabian Oil Company Motorized pump
US11913464B2 (en) 2021-04-15 2024-02-27 Saudi Arabian Oil Company Lubricating an electric submersible pump
US11920469B2 (en) 2020-09-08 2024-03-05 Saudi Arabian Oil Company Determining fluid parameters
US11994016B2 (en) 2021-12-09 2024-05-28 Saudi Arabian Oil Company Downhole phase separation in deviated wells
US12085687B2 (en) 2022-01-10 2024-09-10 Saudi Arabian Oil Company Model-constrained multi-phase virtual flow metering and forecasting with machine learning
US12258954B2 (en) 2021-12-15 2025-03-25 Saudi Arabian Oil Company Continuous magnetic positive displacement pump

Citations (19)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
NL27163C (ru) *
US447909A (en) * 1891-03-10 Ntover
US879476A (en) * 1906-10-25 1908-02-18 Siemens Schuckertwerke Gmbh Centrifugal pump with funnel-shaped guide-pipes in the suction-space between the suction-pipe and ring of blades.
US905712A (en) * 1905-10-23 1908-12-01 Siemens Schuckertwerke Gmbh Centrifugal pump or fan.
US1159094A (en) * 1912-08-19 1915-11-02 Gen Electric Centrifugal air-compressor.
US1159095A (en) * 1915-11-02 Gen Electric Rubbing-strip for centrifugal air-compressors.
US1345638A (en) * 1914-07-13 1920-07-06 Westinghouse Electric & Mfg Co Ventilating apparatus
DE448676C (de) * 1926-01-10 1927-08-25 Gutehoffnungshuette Oberhausen Regelvorrichtung an Kreiselverdichtern
US1728204A (en) * 1927-11-29 1929-09-17 Edge Moor Iron Company Double-flow fan
DE546085C (de) * 1932-03-14 Const C De Raedt Sa Des Atel Vorrichtung zum Verteilen der Luft oder des Gases in einem Ventilator auf die ganze Laenge der Schaufeln
US1896749A (en) * 1930-04-04 1933-02-07 Westinghouse Electric & Mfg Co Stationary blower intake for large turbine generators
US2135053A (en) * 1937-08-24 1938-11-01 John A Rockwell Centrifugal fan
US2305136A (en) * 1941-01-31 1942-12-15 Wright Aeronautical Corp Centrifugal blower construction
CH226523A (de) * 1942-05-04 1943-04-15 Martinka Michael Laufrad für Fliehkraftverdichter.
US2401206A (en) * 1942-08-08 1946-05-28 Bbc Brown Boveri & Cie Centrifugal compressor
US2404609A (en) * 1940-03-02 1946-07-23 Power Jets Res & Dev Ltd Centrifugal compressor
US2405284A (en) * 1942-05-21 1946-08-06 Fed Reserve Bank Centrifugal compressor
US2419669A (en) * 1942-05-08 1947-04-29 Fed Reserve Bank Diffuser for centrifugal compressors
US2438426A (en) * 1939-12-19 1948-03-23 Power Jets Res & Dev Ltd Centrifugal compressor

Patent Citations (19)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE546085C (de) * 1932-03-14 Const C De Raedt Sa Des Atel Vorrichtung zum Verteilen der Luft oder des Gases in einem Ventilator auf die ganze Laenge der Schaufeln
US447909A (en) * 1891-03-10 Ntover
US1159095A (en) * 1915-11-02 Gen Electric Rubbing-strip for centrifugal air-compressors.
NL27163C (ru) *
US905712A (en) * 1905-10-23 1908-12-01 Siemens Schuckertwerke Gmbh Centrifugal pump or fan.
US879476A (en) * 1906-10-25 1908-02-18 Siemens Schuckertwerke Gmbh Centrifugal pump with funnel-shaped guide-pipes in the suction-space between the suction-pipe and ring of blades.
US1159094A (en) * 1912-08-19 1915-11-02 Gen Electric Centrifugal air-compressor.
US1345638A (en) * 1914-07-13 1920-07-06 Westinghouse Electric & Mfg Co Ventilating apparatus
DE448676C (de) * 1926-01-10 1927-08-25 Gutehoffnungshuette Oberhausen Regelvorrichtung an Kreiselverdichtern
US1728204A (en) * 1927-11-29 1929-09-17 Edge Moor Iron Company Double-flow fan
US1896749A (en) * 1930-04-04 1933-02-07 Westinghouse Electric & Mfg Co Stationary blower intake for large turbine generators
US2135053A (en) * 1937-08-24 1938-11-01 John A Rockwell Centrifugal fan
US2438426A (en) * 1939-12-19 1948-03-23 Power Jets Res & Dev Ltd Centrifugal compressor
US2404609A (en) * 1940-03-02 1946-07-23 Power Jets Res & Dev Ltd Centrifugal compressor
US2305136A (en) * 1941-01-31 1942-12-15 Wright Aeronautical Corp Centrifugal blower construction
CH226523A (de) * 1942-05-04 1943-04-15 Martinka Michael Laufrad für Fliehkraftverdichter.
US2419669A (en) * 1942-05-08 1947-04-29 Fed Reserve Bank Diffuser for centrifugal compressors
US2405284A (en) * 1942-05-21 1946-08-06 Fed Reserve Bank Centrifugal compressor
US2401206A (en) * 1942-08-08 1946-05-28 Bbc Brown Boveri & Cie Centrifugal compressor

Cited By (34)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2809493A (en) * 1951-03-19 1957-10-15 American Mach & Foundry Centrifugal flow compressor and gas turbine power plant with a centrifugal flow compressor, toroidal combustion chamber, and centripetal flow turbine
US3058650A (en) * 1955-05-05 1962-10-16 American Radiator & Standard Air conditioner
US3095821A (en) * 1960-05-02 1963-07-02 Elenbaas Herman Sanitary centrifugal pump
US3165257A (en) * 1962-10-03 1965-01-12 Howard C Edwards Pressure inducer
US3289922A (en) * 1964-10-30 1966-12-06 Utah Construction & Mining Co Air compressor
US3365122A (en) * 1966-02-02 1968-01-23 Rotron Mfg Co Centrifugal blower
US4865519A (en) * 1988-02-12 1989-09-12 Institut Of Engineering Thermophysics Of Chinese Academy Of Sciences Oil submersible pump
US5362203A (en) * 1993-11-01 1994-11-08 Lamson Corporation Multiple stage centrifugal compressor
FR2712036A1 (fr) * 1993-11-01 1995-05-12 Lamson Corp Compresseur centrifuge à étages multiples.
US20090208331A1 (en) * 2008-02-20 2009-08-20 Haley Paul F Centrifugal compressor assembly and method
CN101946095A (zh) * 2008-02-20 2011-01-12 特灵国际有限公司 离心式压缩机组件和方法
CN103758789A (zh) * 2008-02-20 2014-04-30 特灵国际有限公司 离心式压缩机组件和方法
US20160273549A1 (en) * 2008-02-20 2016-09-22 Trane International Inc. Centrifugal compressor assembly and method
US9353765B2 (en) * 2008-02-20 2016-05-31 Trane International Inc. Centrifugal compressor assembly and method
US20120121399A1 (en) * 2009-07-31 2012-05-17 Rem Enterprises Inc. air vacuum pump for a particulate loader and transfer apparatus
CN104995411A (zh) * 2012-12-14 2015-10-21 苏尔寿管理有限公司 具有流引导元件的泵送设备
US20150300371A1 (en) * 2012-12-14 2015-10-22 Sulzer Management Ag Pumping apparatus having a flow guiding element
WO2014090559A3 (de) * 2012-12-14 2014-09-25 Sulzer Pumpen Ag Pumpvorrichtung mit einem strömungsleitelement
WO2014090559A2 (de) * 2012-12-14 2014-06-19 Sulzer Pumpen Ag Pumpvorrichtung mit einem strömungsleitelement
US10634165B2 (en) * 2012-12-14 2020-04-28 Sulzer Management Ag Pumping apparatus having a flow guiding element
CN104791254A (zh) * 2015-04-22 2015-07-22 大连深蓝泵业有限公司 大功率轴向剖分双吸两级泵
US10876545B2 (en) * 2018-04-09 2020-12-29 Vornado Air, Llc System and apparatus for providing a directed air flow
US11788391B2 (en) 2018-08-16 2023-10-17 Saudi Arabian Oil Company Motorized pump
US11767741B2 (en) 2018-08-16 2023-09-26 Saudi Arabian Oil Company Motorized pump
US10941778B2 (en) 2018-08-16 2021-03-09 Saudi Arabian Oil Company Motorized pump
US11371326B2 (en) 2020-06-01 2022-06-28 Saudi Arabian Oil Company Downhole pump with switched reluctance motor
US11499563B2 (en) 2020-08-24 2022-11-15 Saudi Arabian Oil Company Self-balancing thrust disk
US11920469B2 (en) 2020-09-08 2024-03-05 Saudi Arabian Oil Company Determining fluid parameters
US11644351B2 (en) 2021-03-19 2023-05-09 Saudi Arabian Oil Company Multiphase flow and salinity meter with dual opposite handed helical resonators
US11591899B2 (en) 2021-04-05 2023-02-28 Saudi Arabian Oil Company Wellbore density meter using a rotor and diffuser
US11913464B2 (en) 2021-04-15 2024-02-27 Saudi Arabian Oil Company Lubricating an electric submersible pump
US11994016B2 (en) 2021-12-09 2024-05-28 Saudi Arabian Oil Company Downhole phase separation in deviated wells
US12258954B2 (en) 2021-12-15 2025-03-25 Saudi Arabian Oil Company Continuous magnetic positive displacement pump
US12085687B2 (en) 2022-01-10 2024-09-10 Saudi Arabian Oil Company Model-constrained multi-phase virtual flow metering and forecasting with machine learning

Also Published As

Publication number Publication date
BE477688A (ru)

Similar Documents

Publication Publication Date Title
US2641191A (en) Guide means on impeller for centrifugal pumps or blowers
US4432694A (en) Blower
US3260443A (en) Blower
US3644056A (en) Centrifugal pump
US3171353A (en) Centrifugal fluid pump
US2727680A (en) Centrifugal fan
US3868196A (en) Centrifugal compressor with rotating vaneless diffuser powered by leakage flow
JPH0262717B2 (ru)
US3986791A (en) Hydrodynamic multi-stage pump
US2471174A (en) Centrifugal compressor stability means
US3531221A (en) Ventilator with axial propeller wheel
GB1171001A (en) Axial Flow Propeller Fan.
US2372880A (en) Centrifugal compressor diffuser vanes
GB712051A (en) Improvements in or relating to axial-flow fluid machines
US3369737A (en) Radial flow machine
US2398203A (en) Centrifugal compressor entry vane
US3059833A (en) Fans
US3876328A (en) Compressor with improved performance diffuser
US2362514A (en) Centrifugal compressor
US2681760A (en) Centrifugal compressor
US3924963A (en) Turbomachine
US4674950A (en) Pitot tube for pitot type centrifugal pump
US2325221A (en) Segregated pressure fan
US1843088A (en) Centrifugal fan
US2441239A (en) Blower apparatus