US3614256A - Combination centrifugal-turbine pump - Google Patents

Combination centrifugal-turbine pump Download PDF

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Publication number
US3614256A
US3614256A US20881A US3614256DA US3614256A US 3614256 A US3614256 A US 3614256A US 20881 A US20881 A US 20881A US 3614256D A US3614256D A US 3614256DA US 3614256 A US3614256 A US 3614256A
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United States
Prior art keywords
turbine
impeller
centrifugal
pumping channel
pumping
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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
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US20881A
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English (en)
Inventor
Leonard J Sieghartner
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.)
Roy E Roth Co
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Roy E Roth Co
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Publication date
Application filed by Roy E Roth Co filed Critical Roy E Roth Co
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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
    • F04D1/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D1/02—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps having non-centrifugal stages, e.g. centripetal
    • 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
    • F04D29/2205—Conventional flow pattern
    • 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
    • F04D29/2205—Conventional flow pattern
    • F04D29/2216—Shape, geometry
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D5/00—Pumps with circumferential or transverse flow
    • F04D5/002—Regenerative pumps

Definitions

  • a centrifugal-turbine pump capable of pumping liquids at or near the boiling point with suction heads not greater than 1 foot having a pump casing with first and second pumping chambers laterally disposed and a drive shaft disposed axially of the pumping chambers.
  • a high-pressure regenerative turbine impeller fixed for rotation with the driving shaft.
  • the second pumping chamber extending angularly about the periphery of the turbine impeller and having a discharge opening radially from the turbine impeller.
  • the casing having a suction entrance for the turbine stage opening laterally from the first pumping channel to the second pumping channel.
  • a centrifugal impeller fixed for rotation within the first channel and with the drive shaft and turbine impeller.
  • This invention relates to a liquid pump for handling liquids at or near the boiling point, and more particularly relates to a combination centrifugal-turbine pump.
  • one object of this invention is to provide a new and improved combination centrifugal-turbine pump having a higher volume capacity with a given casing diameter than is possible with previous designs.
  • Another object of this invention is to provide a new and improved combination centrifugal-turbine pump capable of operating with lower r.p.m. of the rotor to produce the same volume for a given casing diameter than is possible with previous designs.
  • a further object of this invention is to provide a new and improved combination centrifugal-turbine pump having a more uniform radial load balance on the impeller shaft assembly.
  • FIG. I is a longitudinal sectional view illustrating a centrifugal-turbine pump embodying the principles of this invention.
  • FIG. 2 is a sectional view taken along the line 2-2 of FIG. 1 and looking in the direction of the arrows;
  • FIG. 3 is a sectional view taken along the line 3-3 of FIG. 1 and looking in the direction of the arrows;
  • FIG. 4 is a sectional view taken along the line 4-4 of FIG. 3 and looking in the direction of the arrows;
  • FIG. 5 is a sectional view taken along the line 55 of FIG. I and looking in the direction of the arrows;
  • FIG. 6 is a sectional view taken along the line 6--6 of FIG. 5 and looking in the direction of the arrows, illustrating the main body of the pump casing;
  • FIG. 7 is a sectional view taken along the line 77 of FIG. 3 and looking in the direction of the arrows;
  • FIG. 8 is a sectional view taken along the line 88 of FIG. 7 and looking in the direction of the arrows;
  • FIG. 9 is a sectional view taken along the line 9-9 of FIG. 7 and looking in the direction of the arrows;
  • FIG. 10 is a sectional view taken along the line 10-10 of FIG. 8 and looking in the direction of the arrows;
  • FIG. 11 is a sectional view taken along the line l1-lll of FIG. 2 and looking in the direction of the arrows;
  • FIG. 12 is a sectional view taken along the line 12-l2 of FIG. 3 and looking in the direction of the arrows.
  • FIG. I a combination centrifugal-turbine pump having a case, generally designated by the reference numeral 10, which is supported on a frame 12.
  • a case head 14 is secured to the main body 15 of case It) by means of a plurality of cap screws 16.
  • Inboard cover is secured between main body 15 and case extension 17 by means of cap screws 18.
  • a shaft 22 is rotatably supported in the case extension 17.
  • a centrifugal impeller 24 and a turbine impeller 26 are fixed to rotate with the shaft 22 by keys or splines 28 and 30, respectively.
  • the shaft 22 is journaled for rotation in case extension 17 by means of an outboard bearing 32 and an inboard bearing 34, which are lubricated through grease fittings 36 and 38, respectively.
  • An adjusting collar 39 and lock collar 40 provide for positive adjustment of the shaft-impeller assembly.
  • An inner adjusting collar 41 is screwed into an inner housing cap 43 and is locked in position by a setscrew 45 and the split side of the housing cap 43.
  • a spring 47 bears against the bearing outer race 49 of inboard bearing 34 to preload the shaft-impeller assembly toward the shaft extension end.
  • a lip type seal 51 is used to protect the bearings from dirt and liquids.
  • the turbine impeller 26 has vanes. or blades 42 opening from the opposite side and peripherally from the impeller which are operable in a channel 44.
  • the turbine impeller 26 rotates between inner and outer liners 46 and 53 which cooperate with the opposite sides of the impeller 26 to form sealing surfaces 48.
  • a shaft sleeve 50 surrounds the shaft 22 and abuts against the inboard end of the hub 52 of the turbine impeller 26.
  • a stuffing box 56 is disposed between the shaft 22 and the inboard cover 20.
  • a sleeve 58 is placed between the impeller 26 and shaft shoulder and cooperates with a seal rotating unit, having a spring 60, to place the center of the shaft in tension and the sleeves impellers and spacers in compression.
  • No gaskets are needed at the sleeve-shaft shoulder joint to seal, for an excellent finish on both sleeve and shaft shoulders combined with high loading per square inch effectively stops leaks of liquids or gasses at this joint.
  • the seal shown is a balanced type of seal but any other type of seal or packing may be used to suit the liquid and pumping conditions.
  • An annular stationary bushing 70 is disposed within the case 110 and surrounds the hub 72 of the centrifugal impeller 24 and an impeller spacer 74.
  • the centrifugal impeller 24 is held on the end of the shaft 22 by means of a nut 76.
  • the stationary bushing 70 acts in conjunction with a ring 77, which is driven by pins 78 extending into the turbine impeller 26 to prevent leakage of high-pressure liquid back into the low pressure centrifugal case.
  • An annular groove 69 cut into the l. D. bushing 70 is connected by a passageway 7I of outboard cover 103 to a low-pressure point in the turbine working channel about l5 from the suction entrance to the turbine stage.
  • Centrifugal impeller 24 has a one-piece housing 80 (FIGS. II and 7) having an inner annular rim portion 82, an intermediate flared skirt portion 84, and an outer annular rim portion 86.
  • An inlet opening 88 is formed in the inner end of the housing 80 and is in direct communication with inlet opening 90 of case head 14.
  • the inlet opening 90 is very large as compared with the overall diameter of impeller 24.
  • the inner rim portion is rotatably supported by a bushing 92 seated in an annular groove 94 at the outer end of cylindrical wall 96 which defines inlet opening 90.
  • a circular wall 98 having a central hub 72.
  • Centrifugal impeller 24 has three equally spaced discharge openings 1M) (FIGS. 3, 4 and 7) which are formed in the peripheral surface of outer rim portion 86 of housing 80. These discharge openings 100 are in direct communication with volute channel 102 extending generally angularly about and spaced outwardly from the periphery of the centrifugal impeller 24.
  • the centrifugal impeller provided in the pump of this invention is of a special type having a very low-pressure creating characteristic and a higher volumetric efficiency as compared with prior centrifugal impeller designs.
  • a higher volumetric efficiency is possible by virtue of the deep blades 104 (FIG. 3) having a particular design formed in centrifugal impeller 24.
  • Blades 104 are in equal space relation about the center of wall 98 and the axis of shaft 22 and have identical shapes.
  • Each blade 104 comprises an outer curved portion 106 extending perpendicular from plate 98, having a constant axial width and an inner curved portion 108 gradually increasing in axial width from the center of centrifugal impeller 24 in a diverging outward direction towards the opposite ends of the outer curved portion 106.
  • the outer curved portion 106 comprises a first arcuate segment 107 with an outer surface concentric with the center of impeller 24, and a second arcuate segment 109 extending inwardly from one end of the first arcuate segment 107 a short distance so as to leave a space between its innermost end and the center of impeller 24.
  • first arcuate segment 107 of the three outer curved portions 106 form the outer annular rim portion 86 of housing 80 and the spacing between adjacent segments 107 defines discharge outlets 100 for centrifugal impeller 24.
  • the liquid entering inlet 88 impinges against rotating circular plate 98 and is smoothly directed outwardly along the inner curved portions 108 and outer curved portions of blades 104 to the three discharge outlets 100 into volute channel 102.
  • the impeller blades 104 are arranged so that the liquid is more restricted in leaving the discharge outlets 100 than the liquid entering through inlet 88 so that nowhere in impeller 24 is there a drop in pressure, but rather a steady increase in pressure with the least possible disturbance.
  • the particular shape of blades 104, with the inner curved portion 108 tapering down to the center of impeller 24 aids the impeller pressure buildup.
  • Volute channel 102 has a specially designed interior for guiding a large volume of liquid at the boiling point from the three outlets 100 of centrifugal impeller 24 into the channel 44 of the turbine stage. To prevent boiling of the liquid being pumped, it is essential that the volute channel 102 be designed to avoid any disturbance being introduced to the liquid.
  • the volute channel 102 is formed in the case head and enclosed at its outer end by main body 15 of case and outboard cover 103.
  • a cavity 116 is formed in case head 14 to define volute channel 102 and extends laterally away from outboard cover 103 and discharge outlets 100 of centrifugal impeller 24.
  • Extending generally perpendicular from wall 114 of the cavity 116 are three equally spaced diffuser vanes 118 (FIGS. 2 and 3). These vanes 118 have at their outer end 117 a generally spherical cross section with a cutout 120 to accommodate the outer rim portion 86 of the centrifugal impeller 24.
  • the base 119 of the three vanes 118 are supported on a slanting wall 122 which diverges outwardly from the rear wall 114.
  • the cavity 116 gradually increases in volume from its closed end 124 to its open end 126.
  • an inclined block 130 is provided which extends forwardly from the rear wall 114 of the cavity 116.
  • the inclined block 130 directs the liquid from the impeller stage forwardly to the entrance 131 to channel 44 of the turbine stage.
  • the inclined block or guide ramp 130 for directing the liquid into the turbine stage extends at an obtuse angle away from the innermost wall 114 towards the outer end of the cavity 116 formed in the case head 14.
  • Diffuser vanes 118 provide an important function in the operation of the centrifugal stage, for they serve to straighten the flow of liquid exiting from discharge outlets 100 of centrifugal impeller 24. By virtue of their close proximity to the outer rim portion 86 of impeller 24, diffuser vanes 118 also provide for multiple outlets for impeller 24 resulting in a more uniform radial load balance on the impeller shaft assembly.
  • the face 140 of main body in opposing relation with the case head 14 has a shallow cavity 142 having an identical cross-sectional shape to cavity 116 in case head 14.
  • a slightly inclining surface 144 (FIG. 12) is provided which mates with inclined block (FIG. 11) to guide the liquid into the turbine stage.
  • Channel 146 which is formed in the main body 15 of casing 10, provides a passageway for the liquid into liquid channel 44, which is formed about the outer periphery of turbine impeller 26 between inner and outer liners 46 and 53.
  • a baffle 148 is placed across the suction of the turbine stage by forming the baffle 148 integral with the main body 15 (see FIG. 6) and in position extending across the inlet to channel 44.
  • the particular baffle 148 illustrated in the drawing is shown of tapered form, with its tapering sides 150 converging outwardly to a relatively sharp edge. Baffle 148 prevents the liquid thrown from turbine impeller 26 from interfering with the incoming liquid.
  • an outlet 154 for the turbine stage which is in direct communication with liquid channel 44.
  • a pair of block members 156 are integrally formed with inner and outer liners 46 and 53 to interrupt liquid channel 44.
  • the liquid enters the suction entrance or inlet 88 of the centrifugal impeller 24 and is discharged through outlets 100 from the periphery of centrifugal impeller 24 into the volute channel 102 at increased pressure and higher velocity.
  • the liquid discharged from outlets 100 impinges against vanes 118, which serve to straighten the flow.
  • the liquid is directed to the rear wall 114 of cavity 118 in a swirling motion towards inclined block 130, where the liquid is guided towards suction entrance 131 of the turbine stage.
  • the liquid then passes through suction entrance 131 into the annular liquid channel 44 of the turbine stage.
  • the regenerative pumping action of turbine impeller 26 builds up sufficient pressure to deliver the liquid to the outlet 154 of the turbine stage, by constant recirculation of the liquid through the impeller vanes 42 and annular channel 44.
  • An improved centrifugal-turbine pump capable of pumping liquids and liquified gases at or near the boiling point thereof with suction heads not greater than about I foot, having a pump casing with a first pumping channel and a second pumping channel disposed laterally of said first pumping channel, a drive shaft disposed axially of said pumping channels, a high-pressure regenerative turbine impeller fixed for rotation with said driving shaft, said second pumping channel extending generally angularly about and spaced outwardly from the periphery of said turbine impeller and having a discharge opening generally radially from said turbine impeller, said casing having a suction entrance for the turbine stage opening laterally from said first pumping channel to said second pumping channel, and a centrifugal impeller fixed for rotation within said first pumping channel and with said driving shaft and turbine impeller, said centrifugal impeller having a large diameter axial inlet opening of substantially the same as a suction inlet for the centrifugal stage defined by said casing, said centrifug
  • said first pumping channel is defined by a cavity in said casing extending laterally away from said turbine stage to a rear wall with the area of said cavity annular about the periphery of said centrifugal impeller and increasing in volume between a closed end and an open end, and an axially inclined block in said cavity between said rear wall and said suction entrance for the turbine stage to guide the liquid into said turbine stage.
  • said first pumping channel further includes a plurality of spaced diffuser vanes extending from said rear wall towards said turbine stage and disposed in close proximity to said periphery of said centrifugal impeller to straighten the flow of liquid exiting from said discharge outlets of said centrifugal impeller.
  • An improved centrifugal-turbine pump capable of pumping liquids and liquified gases at or near the boiling point thereof with suction heads not greater than about 1 foot, having a pump casing with a first pumping channel and a second pumping channel disposed laterally of said first pumping channel, a drive shaft disposed axially of said pumping channels, a high pressure regenerative turbine impeller fixed for rotation with said driving shaft, said second pumping channel extending generally angularly about and spaced outwardly from the periphery of said turbine impeller and having a discharge opening generally radially from said turbine impeller, said casing having a suction entrance for the turbine stage opening laterally from said first pumping channel to said second pumping channel and a centrifugal impeller fixed for rotation within said first pumping channel and with said driving shaft and turbine impeller, said centrifugal impeller having a large diame' ter axial inlet opening of substantially the same as a suction inlet for the centrifugal stage defined by said casing, said
  • said first pumping channel further includes a plurality of spaced diffuser vanes extending from said rear wall towards said turbine stage and disposed in close proximity to said periphery of said centrifugal impeller to straighten the flow of liquid exiting from said discharge outlets of said centrifugal impeller.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Geometry (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
US20881A 1970-03-19 1970-03-19 Combination centrifugal-turbine pump Expired - Lifetime US3614256A (en)

Applications Claiming Priority (1)

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US2088170A 1970-03-19 1970-03-19

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US20881A Expired - Lifetime US3614256A (en) 1970-03-19 1970-03-19 Combination centrifugal-turbine pump

Country Status (7)

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US (1) US3614256A (fr)
JP (1) JPS5429721B1 (fr)
BE (1) BE762867A (fr)
CA (1) CA945812A (fr)
CH (1) CH531649A (fr)
DE (1) DE2113083C2 (fr)
GB (1) GB1339986A (fr)

Cited By (19)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3770991A (en) * 1972-02-29 1973-11-06 Federal Mogul Corp High speed air pressure sensitive seal and bearing system
US3892498A (en) * 1973-11-28 1975-07-01 Jacuzzi Research Inc Fluid pump with rotary seal assembly
JPS56175956U (fr) * 1980-05-30 1981-12-25
JPS5713300A (en) * 1980-06-03 1982-01-23 Roth Co Roy E Centrifugal impeller
US4479756A (en) * 1978-08-21 1984-10-30 Roy E. Roth Company Multi-stage pump
US4726734A (en) * 1984-07-12 1988-02-23 Sero Pumpenfabrik Gmbh Centrifugal pump
US4927327A (en) * 1986-08-16 1990-05-22 Bbc Brown Boveri Ag Contactless centrifugal seal device for a rotating machine part
US5096386A (en) * 1989-11-17 1992-03-17 Sundstrand Corporation Integral liquid ring and regenerative pump
US5238253A (en) * 1991-04-22 1993-08-24 Roy E. Roth Company Regenerative turbine flow inducer for double or tandem mechanical seals
US5295784A (en) * 1991-08-24 1994-03-22 Durr Dental Gmbh & Co. Kg Suction device, especially for use in dentistry
US5435691A (en) * 1993-02-13 1995-07-25 Robert Bosch Gmbh Aggregate for feeding fuel from supply tank to internal combustion engine of motor vehicles
US6668556B2 (en) 2002-04-18 2003-12-30 Eco Oxygen Technologies, Llc. Gas transfer energy recovery and effervescence prevention apparatus and method
US6921245B2 (en) 2003-02-11 2005-07-26 Envirotech Pumpsystems, Inc. Coaxial seal for a pump
US7320749B2 (en) 2004-02-09 2008-01-22 Eco-Oxygen Technologies, Llc Method and apparatus for control of a gas or chemical
US7566397B2 (en) 2004-02-09 2009-07-28 Eco Oxygen Technologies, Llc Superoxygenation of raw wastewater for odor/corrosion control
US11193504B1 (en) 2020-11-24 2021-12-07 Aquastar Pool Products, Inc. Centrifugal pump having a housing and a volute casing wherein the volute casing has a tear-drop shaped inner wall defined by a circular body region and a converging apex with the inner wall comprising a blocker below at least one perimeter end of one diffuser blade
CN114109906A (zh) * 2020-08-26 2022-03-01 上海连成（集团）有限公司 一种用于多级泵的蜗壳式吐出段结构和多级泵
USD946629S1 (en) 2020-11-24 2022-03-22 Aquastar Pool Products, Inc. Centrifugal pump
USD986289S1 (en) 2020-11-24 2023-05-16 Aquastar Pool Products, Inc. Centrifugal pump

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2204917B (en) * 1987-05-19 1992-01-08 Apv Uk Centrifugal pump
DE10120409B4 (de) * 2001-04-26 2004-02-12 Sero Pumpenfabrik Gmbh & Co. Kg Kreiselpumpe zur Förderung heißer Medien
DE102005060895B4 (de) * 2005-12-20 2012-07-19 Sero Pumpsystems Gmbh Kreiselpumpe zur Förderung heißer und/oder leicht ausgasender und/oder gasbeladener Medien
CN105626544B (zh) * 2016-03-22 2018-01-09 广东凌霄泵业股份有限公司 一种卧式多级离心泵
CN109340175A (zh) * 2018-11-21 2019-02-15 中国航发西安动力控制科技有限公司 一种带旋涡周缘叶片的离心组合叶轮

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE711791C (de) * 1938-04-28 1941-10-07 Anna Dickow Geb Driemeyer Anordnung des Antriebes fuer eine nicht selbstansaugende Kreiselpumpe
US2368530A (en) * 1943-04-19 1945-01-30 Edwards Miles Lowell Vapor expelling pump
US2875698A (en) * 1959-03-03 Combination centrifugal-turbine pump
US3154020A (en) * 1962-04-05 1964-10-27 Roth Co Roy E Sealing means for rotary pump shafts and the like
US3247797A (en) * 1962-04-05 1966-04-26 Roth Co Roy E Sealing means for rotary pump shafts and the like
US3261297A (en) * 1965-05-24 1966-07-19 William H Daniel Pump
US3385225A (en) * 1965-06-29 1968-05-28 Siemen & Hinsch Gmbh Rotary pump

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1072481B (fr) *
US1012265A (en) * 1910-05-31 1911-12-19 Charles E Pellow Centrifugal pump.
US2165808A (en) * 1937-05-22 1939-07-11 Murphy Daniel Pump rotor
US2956504A (en) * 1951-11-15 1960-10-18 Nash Engineering Co Booster pumps
DE1152887B (de) * 1955-03-16 1963-08-14 Roth Co Roy E Mehrstufige Pumpe zum Foerdern von siedenden oder nahezu siedenden Fluessigkeiten bzw. verfluessigten Gasen
US3036799A (en) * 1959-10-16 1962-05-29 Martin James Means for releasing a subsidiary body from a main body in flight

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2875698A (en) * 1959-03-03 Combination centrifugal-turbine pump
DE711791C (de) * 1938-04-28 1941-10-07 Anna Dickow Geb Driemeyer Anordnung des Antriebes fuer eine nicht selbstansaugende Kreiselpumpe
US2368530A (en) * 1943-04-19 1945-01-30 Edwards Miles Lowell Vapor expelling pump
US3154020A (en) * 1962-04-05 1964-10-27 Roth Co Roy E Sealing means for rotary pump shafts and the like
US3247797A (en) * 1962-04-05 1966-04-26 Roth Co Roy E Sealing means for rotary pump shafts and the like
US3261297A (en) * 1965-05-24 1966-07-19 William H Daniel Pump
US3385225A (en) * 1965-06-29 1968-05-28 Siemen & Hinsch Gmbh Rotary pump

Cited By (24)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3770991A (en) * 1972-02-29 1973-11-06 Federal Mogul Corp High speed air pressure sensitive seal and bearing system
US3892498A (en) * 1973-11-28 1975-07-01 Jacuzzi Research Inc Fluid pump with rotary seal assembly
US4479756A (en) * 1978-08-21 1984-10-30 Roy E. Roth Company Multi-stage pump
JPS56175956U (fr) * 1980-05-30 1981-12-25
JPS5713300A (en) * 1980-06-03 1982-01-23 Roth Co Roy E Centrifugal impeller
US4726734A (en) * 1984-07-12 1988-02-23 Sero Pumpenfabrik Gmbh Centrifugal pump
US4927327A (en) * 1986-08-16 1990-05-22 Bbc Brown Boveri Ag Contactless centrifugal seal device for a rotating machine part
US5096386A (en) * 1989-11-17 1992-03-17 Sundstrand Corporation Integral liquid ring and regenerative pump
US5238253A (en) * 1991-04-22 1993-08-24 Roy E. Roth Company Regenerative turbine flow inducer for double or tandem mechanical seals
US5295784A (en) * 1991-08-24 1994-03-22 Durr Dental Gmbh & Co. Kg Suction device, especially for use in dentistry
US5435691A (en) * 1993-02-13 1995-07-25 Robert Bosch Gmbh Aggregate for feeding fuel from supply tank to internal combustion engine of motor vehicles
US6848258B1 (en) 2002-04-18 2005-02-01 Eco-Oxygen Technologies, Llc Gas transfer energy recovery and effervescence prevention apparatus and method
US6668556B2 (en) 2002-04-18 2003-12-30 Eco Oxygen Technologies, Llc. Gas transfer energy recovery and effervescence prevention apparatus and method
US6921245B2 (en) 2003-02-11 2005-07-26 Envirotech Pumpsystems, Inc. Coaxial seal for a pump
US7320749B2 (en) 2004-02-09 2008-01-22 Eco-Oxygen Technologies, Llc Method and apparatus for control of a gas or chemical
US7566397B2 (en) 2004-02-09 2009-07-28 Eco Oxygen Technologies, Llc Superoxygenation of raw wastewater for odor/corrosion control
US8580125B2 (en) 2004-02-09 2013-11-12 Eco Oxygen Technologies, Llc Method and apparatus for control of a gas or chemical
CN114109906A (zh) * 2020-08-26 2022-03-01 上海连成（集团）有限公司 一种用于多级泵的蜗壳式吐出段结构和多级泵
US11193504B1 (en) 2020-11-24 2021-12-07 Aquastar Pool Products, Inc. Centrifugal pump having a housing and a volute casing wherein the volute casing has a tear-drop shaped inner wall defined by a circular body region and a converging apex with the inner wall comprising a blocker below at least one perimeter end of one diffuser blade
USD946629S1 (en) 2020-11-24 2022-03-22 Aquastar Pool Products, Inc. Centrifugal pump
US11408441B1 (en) 2020-11-24 2022-08-09 Aquastar Pool Products, Inc. Centrifugal pump
USD971966S1 (en) 2020-11-24 2022-12-06 Aquastar Pool Products, Inc. Centrifugal pump
USD986289S1 (en) 2020-11-24 2023-05-16 Aquastar Pool Products, Inc. Centrifugal pump
US11668329B1 (en) 2020-11-24 2023-06-06 Aquastar Pool Products, Inc. Centrifugal pump

Also Published As

Publication number Publication date
BE762867A (fr) 1971-07-16
DE2113083C2 (de) 1985-04-25
GB1339986A (en) 1973-12-05
DE2113083A1 (de) 1971-10-07
CA945812A (en) 1974-04-23
JPS5429721B1 (fr) 1979-09-26
CH531649A (de) 1972-12-15

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