US20100111680A1 - Delivery Pump - Google Patents

Delivery Pump Download PDF

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Publication number
US20100111680A1
US20100111680A1 US12/607,683 US60768309A US2010111680A1 US 20100111680 A1 US20100111680 A1 US 20100111680A1 US 60768309 A US60768309 A US 60768309A US 2010111680 A1 US2010111680 A1 US 2010111680A1
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US
United States
Prior art keywords
pump
impeller
delivery
delivery pump
centrifugal
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.)
Abandoned
Application number
US12/607,683
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English (en)
Inventor
Axel Binder
Christoph Jaeger
Christoph Keller
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.)
KSB AG
Original Assignee
KSB AG
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 KSB AG filed Critical KSB AG
Assigned to KSB AKTIENGESELLSCHAFT reassignment KSB AKTIENGESELLSCHAFT ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: BINDER, AXEL, KELLER, CHRISTOPH, JAEGER, CHRISTOPH
Publication of US20100111680A1 publication Critical patent/US20100111680A1/en
Abandoned legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D15/00—Control, e.g. regulation, of pumps, pumping installations or systems
    • F04D15/0066—Control, e.g. regulation, of pumps, pumping installations or systems by changing the speed, e.g. of the driving engine
    • 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
    • F04D29/2238—Special flow patterns
    • F04D29/225—Channel wheels, e.g. one blade or one flow channel
    • 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
    • F04D29/58—Cooling; Heating; Diminishing heat transfer
    • F04D29/586—Cooling; Heating; Diminishing heat transfer specially adapted for liquid pumps
    • F04D29/588—Cooling; Heating; Diminishing heat transfer specially adapted for liquid pumps cooling or heating the machine

Definitions

  • the invention relates to a delivery pump with a variable-speed drive, the delivery pump being designed as a single-stage centrifugal pump with a radial impeller ( 2 ) of centrifugal type of construction, arranged rotatably in an impeller chamber of a pump casing ( 1 ), for delivering a fluid between a pump inlet ( 4 ) and a pump outlet ( 13 ), the radial impeller ( 2 ) being connected to a drive motor variable in speed into the five-digit range of revolutions per minute, the radial impeller ( 2 ) receiving the flow centrally, being provided with delivery ducts ( 3 ) and, in the case of an outside diameter of up to 55 mm, delivery heads of up to 300 m.
  • Such plants require an accurate, constant, freely adjustable and pulsation-fee volume flow of liquid substances.
  • positive-displacement pumps in the form of micro-annular and gear pumps and also in the form of diaphragm and piston pumps are employed.
  • Such positive-displacement pumps have the disadvantage of the lack of reliability due to friction between the components to be sealed off, moved in relation to one another, and their pulsating delivery stream. A resulting outlay in terms of maintenance and the costs for wearing parts and for exchanging these are detrimental to rapid research and development work and appreciably disrupt a production process.
  • a centrifugal pump designed as a canned motor pump, for the circulation of supercritical hydrocarbons is known from WO 2005/052365 A2.
  • the drive motor has a can made from polyaryletheretherketone (PEEK), within which is arranged a rotor protected by a high-grade steel covering. Ceramic bearings of the pump shaft and of the drive rotor are lubricated by a part stream of the delivery fluid, said part stream being extracted from the pump casing.
  • the impeller of open design has a diameter of between 1 and 2 inches
  • the impeller-driving rotor of the rolling bearing-mounted direct-current motor has a diameter of between 1.5 and 2 inches.
  • the single-stage pumping arrangement with the open impeller is intended to reach maximum rotational speeds of up to 60,000 rpm.
  • the suction connection piece, the pressure connection piece and a type of spiral chamber following the impeller are arranged in an outer pump casing part, while an inner pump casing part has the overhung-mounted impeller and a fastening for a variable-speed direct-current canned motor as a drive motor.
  • Another object of the invention is to provide a delivery pump for the delivery and/or metering of milliliter amounts of liquid chemical, pharmaceutical and/or cosmetic components.
  • a further object of the invention is to provide a pump unit having a delivery rate which is variable, pulsation-free and accurately adjustable over a wide range for delivering differing media having different properties.
  • An additional object of the invention is to provide a delivery pump which which can be cleaned easily for rapid product changes.
  • a metering pump in the form of a centrifugal pump having a centrifugal pump construction is produced.
  • This is designed as a delivery pump for use in a process engineering plant for nominal operation in the form of continuous centrifugal pump part-load operation with delivery rates in the range of 0 ml/min to 7000 ml/min, nominal operation being characterized by a centrifugal pump part-load-specific rotational speed nq TL ⁇ 0.05 ⁇ 10, and the impeller chamber being provided on the circumference with one or more pump outlet ducts arranged at an acute angle to or tangentially to the radial impeller outside diameter.
  • this centrifugal pump is designed for extreme part-load operation, with the result that small quantities are delivered, pulsation-free.
  • the delivery pump preferably has a centrifugal pump part-load-specific rotational speed nq TL ⁇ 0.05 ⁇ 3 (l/min). It also has proved advantageous to design the delivery pump for a centrifugal pump part-load operating range nq TL ⁇ 2.5 has also proved advantageous.
  • the radial impeller may have a maximum outside diameter of up to 70 mm.
  • the pump casing with a radial impeller arranged in it, preferably has a residual volume lower than 30 milliliters.
  • This has the considerable advantage that the delivery pump is easily scavengable.
  • an inside diameter of the impeller chamber is designed to be a maximum of 4% larger than an outside diameter of the radial impeller.
  • the inlet ports of one or more pump outlet ducts are constructed in the form of pressure tubes or similarly to a pressure tube.
  • the pump is provided with a thermal control device, preferably for nominal operation at a centrifugal pump part-load-specific rotational speed nq TL ⁇ 0.05 ⁇ 1 (l/min).
  • This device improves the delivery of sensitive fluids and/or of fluids with a low boiling point by means of the delivery pump capable of being operated in a wide nq TL range.
  • a seal is arranged between the impeller chamber and the radial impeller and/or its shaft.
  • a design is likewise possible in which a hermetically leaktight magnet-coupled drive transmits a torque to the radial impeller.
  • a bearing for the shaft is arranged on the pump casing, on the thermal control casing and/or on a bearing casing.
  • the delivery pump may be constructed as a modular assembly with a flanged-on motor.
  • the delivery pump is characterized by constant delivery operation or by metered dosing operation.
  • FIG. 1 shows a longitudinal sectional view of a delivery pump according to the invention
  • FIG. 2 shows a perspective view of the pump unit
  • FIG. 3 shows a perspective view of an impeller
  • FIG. 4 shows a sectional view of the impeller
  • FIG. 5 shows a cross-sectional view through the delivery pump
  • FIG. 6 shows the position of the delivery pump in an nq graph.
  • FIG. 1 illustrates a delivery pump having a single-stage pump construction.
  • a radial impeller 2 of centrifugal type of construction is arranged rotatably in the pump casing 1 .
  • the radial impeller 2 has delivery ducts 3 and receives the flow centrally through a pump inlet 4 .
  • the radial impeller 2 is connected in a force-transmitting manner to a variable-speed drive 5 and has an outside diameter D LA which may amount to up to 70 mm.
  • the radial impeller rotates in an impeller chamber 6 , the inside diameter D LRI of which is designed to be only a maximum of 4% larger than the outside diameter D LA , of the radial impeller 2 .
  • the pump casing 1 is provided with a thermal control device 7 which in this illustrative embodiment is integrated in the pump casing. Other forms of construction are also possible. Cooling spaces 7 . 1 to 7 . 3 surround the impeller chamber 6 and also a seal casing 8 contiguous to the pump casing 1 . Within the seal casing 8 is arranged, as a type of shaft seal, a seal 9 which is illustrated in the illustrative embodiment as a lip sealing ring. Depending on the delivery fluid used, the seal 9 may also be constructred as a floating ring seal. The seal 9 may bear sealingly against the impeller 2 , against an impeller hub 2 . 1 or against the shaft 10 , depending on the selected connection between the impeller and a shaft 10 of the drive.
  • the thermal control spaces 7 . 1 to 7 . 3 are acted upon by external coolant.
  • the parts of the pump casing which are touched by the delivery fluid are reliably cooled, since the centrifugal pump is designed for continuous operation in a part-load operating point map, the delivery rate limits of which lie in the range of 0 milliliters/min to 3600 milliliters/min in the case of a delivery head limit of 20 meters-300 meters.
  • additional coolant 11 is arranged on the outer circumference of the drive 5 .
  • the drive 5 is also connected or attached in a force-transmitting manner to the thermal control device 7 .
  • the area of the pump inlet 4 is defined by a bearing face 12 which is located in the immediate vicinity of the pump interior and against which a line to be connected for a delivery fluid bears sealingly.
  • a similar construction is present at the pump outlet 13 which here is located below the drawing plane and can be seen only partially as a semicircle.
  • the fastening of pump lines, not shown here, which are to be connected thereto takes place in a known manner, for example via union nuts.
  • FIG. 2 is a perspective view of the delivery pump constructed as a unit.
  • the thermal control device 7 is integrated into the pump casing 1 , and the pump inlet 4 and pump outlet 13 extend through the thermal control device 7 as far as the impeller chamber.
  • External thermal control means for example coolants, are supplied to and discharged from the thermal control spaces 7 . 1 to 7 . 3 via the axial or radial connections 14 , 15 which can be used selectively.
  • a pump unit and drive motor 5 are combined into a structural unit and are held in a carrying element 16 .
  • the carrying element 16 satisfies the precondition for modular construction or installation into an existing plant.
  • FIG. 3 shows a perspective view of a radial impeller 2 .
  • the radial impeller 2 is of disk-shaped configuration and in this example is provided with a hub 2 . 1 .
  • a force-transmitting connection to the shaft 10 , not shown, of the drive 5 takes place within the hub 2 . 1 .
  • Delivery ducts 3 are arranged inside the radial impeller 2 .
  • a plurality of delivery depressions 18 which are configured in the form of blind bores, are arranged on the impeller circumference 17 . With the aid of these delivery depressions, the pressure coefficient of the centrifugal pump impeller is improved.
  • the pressure-side and suction-side cover disks 19 , 20 have a plurality of radially extending delivery grooves 21 .
  • the delivery grooves 21 likewise improve the pressure coefficient of an impeller installed according to FIG. 1 in an impeller chamber 6 .
  • Compensating bores 22 which extend through the impeller in the axial direction serve for pressure compensation within the pump casing and at the same time as a mounting aid when a connection to the drive is being made.
  • FIG. 4 shows a sectional view through an impeller 2 in which four delivery ducts 3 are used. Their diameter is coordinated such that they do not intersect an adjacent delivery duct in the region of the impeller inlet 23 . This ensures that a defined impeller inlet diameter is maintained.
  • the depth T of the delivery depressions 18 is selected as a function of the desired residual volume of a ready-assembled pump.
  • any other form, for example grooves, slots or the like, by means of which energy transmission is possible in the region of the impeller outside diameter, may also be employed.
  • FIG. 5 shows a cross section through the delivery pump of the invention. Due to the generously dimensioned thermal control space 7 . 2 which is operatively connected to the other thermal control space, continuous extreme part-load operation is ensured.
  • the pump outlet duct 13 may be configured as a simple bore or, as illustrated, it may be formed by an insert 24 resembling a pressure tube and having an inlet port 25 . The latter makes simple adaptation to varied design requirements possible.
  • a radial gap width which lies in the single-digit millimeter range is obtained between the outside diameter D LA , of the radial impeller and the enveloping surrounding diameter D LRI of the impeller chamber 6 .
  • the radial gap between the impeller and casing lies in the region of 2 mm.
  • the gap between the impeller and casing lies in a similar order of magnitude in the region of the axial impeller sides.
  • the circumferential component of the impeller simultaneously approaches the circumferential speed, and, in combination with a pump outlet 13 arranged at an oblique angle, preferably tangentially, to the impeller 2 , a maximum possible dynamic pressure is obtained for this centrifugal pump at its outlet port.
  • high delivery heads along with a minimal residual volume within the pump casing, can be achieved.
  • the contact-free arrangement of the impeller within the impeller chamber avoids frictional surfaces bearing sealingly one against the other. This measure prevents the generation of mechanical frictional heat, prevents frictional wear and resulting contamination of a delivery fluid with abraded particles and improves operational reliability due to substantially prolonged service lives. Moreover, sealing gaps which adversely affect cleanability are avoided.
  • the nq values of centrifugal pumps are compared with those of positive-displacement pumps in an nq graph in characteristic maps depicted by unbroken lines.
  • the novel delivery pump, with its characteristic map, illustrated in gray, of the centrifugal pump part-load-specific rotational speed nq TL covers the range between these two opposite pump types for the first time.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
US12/607,683 2007-04-28 2009-10-28 Delivery Pump Abandoned US20100111680A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102007020218.2 2007-04-28
DE102007020218A DE102007020218A1 (de) 2007-04-28 2007-04-28 Förderpumpe
PCT/EP2008/002767 WO2008131846A1 (de) 2007-04-28 2008-04-08 Förderpumpe

Related Parent Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2008/002767 Continuation WO2008131846A1 (de) 2007-04-28 2008-04-08 Förderpumpe

Publications (1)

Publication Number Publication Date
US20100111680A1 true US20100111680A1 (en) 2010-05-06

Family

ID=39651186

Family Applications (1)

Application Number Title Priority Date Filing Date
US12/607,683 Abandoned US20100111680A1 (en) 2007-04-28 2009-10-28 Delivery Pump

Country Status (9)

Country Link
US (1) US20100111680A1 (zh)
EP (1) EP2142804A1 (zh)
JP (1) JP2010525223A (zh)
CN (1) CN101680456A (zh)
AU (1) AU2008243437A1 (zh)
DE (1) DE102007020218A1 (zh)
TW (1) TW200916660A (zh)
WO (1) WO2008131846A1 (zh)
ZA (1) ZA200905469B (zh)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20120011857A1 (en) * 2009-03-24 2012-01-19 Concepts Eti, Inc. High-Flow-Capacity Centrifugal Hydrogen Gas Compression Systems, Methods and Components Therefor
US20150168342A1 (en) * 2011-02-15 2015-06-18 Michael A. Silveri Amperometric Sensor System
US9568921B2 (en) 2012-11-15 2017-02-14 Abb Technology Oy Method for approximating a static head of a fluid transfer system
CN112253481A (zh) * 2019-10-25 2021-01-22 李亨馥 高性能卫生泵

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102465882A (zh) * 2010-11-10 2012-05-23 上海福思特流体机械有限公司 一种改进叶轮布置的多级离心泵
CN107165835B (zh) * 2017-06-20 2018-11-30 广东河海泵业机械有限公司 具有紧凑布局位移传感仪的机械式水泵叶片角度调节装置

Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1988875A (en) * 1934-03-19 1935-01-22 Saborio Carlos Wet vacuum pump and rotor therefor
US3205828A (en) * 1963-08-23 1965-09-14 Gorman Rupp Co High efficiency low specific speed centrifugal pump
US3396220A (en) * 1961-05-26 1968-08-06 Defence Uk Manufacture of ceramic articles
US3647314A (en) * 1970-04-08 1972-03-07 Gen Electric Centrifugal pump
US3816020A (en) * 1972-10-19 1974-06-11 Selgo Pumps Inc Pump
US5106263A (en) * 1989-09-22 1992-04-21 Jidosha Denki Kogyo K.K. Centrifugal pump with high efficiency impeller
US5257910A (en) * 1988-12-23 1993-11-02 Ksb Aktiengesellschaft Centrifugal pump impeller with a low specific speed of rotation
US5451139A (en) * 1992-01-24 1995-09-19 Ebara Corporation Self priming centrifugal
US5540550A (en) * 1994-01-21 1996-07-30 Nikkiso Co., Ltd. Solid impeller for centrifugal pumps
US20040062647A1 (en) * 2002-09-26 2004-04-01 Garrett Norman H. Roto-dynamic fluidic systems
US6779965B2 (en) * 2002-04-26 2004-08-24 Schlumberger Technology Corporation Integrated axial flow pump

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE853386C (de) * 1941-03-26 1952-10-23 Henschel & Sohn G M B H Schnellaufende Hochdruck-Schleuderpumpe
US3936220A (en) * 1974-08-26 1976-02-03 Controls Southeast, Inc. Jacket construction for fluid-circulating pumps
DE3639719C3 (de) * 1986-11-20 1994-02-24 Hermetic Pumpen Gmbh Spaltrohrmagnetpumpe
DE4309697A1 (de) * 1993-03-25 1994-09-29 Hilge Philipp Gmbh Verfahren zum hydrodynamischen Transportieren von oxidationsempfindlichen Flüssigkeiten sowie Anlage und Pumpe hierfür
US6986647B2 (en) 2003-11-21 2006-01-17 Tokyo Electron Limited Pump design for circulating supercritical carbon dioxide

Patent Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1988875A (en) * 1934-03-19 1935-01-22 Saborio Carlos Wet vacuum pump and rotor therefor
US3396220A (en) * 1961-05-26 1968-08-06 Defence Uk Manufacture of ceramic articles
US3205828A (en) * 1963-08-23 1965-09-14 Gorman Rupp Co High efficiency low specific speed centrifugal pump
US3647314A (en) * 1970-04-08 1972-03-07 Gen Electric Centrifugal pump
US3816020A (en) * 1972-10-19 1974-06-11 Selgo Pumps Inc Pump
US5257910A (en) * 1988-12-23 1993-11-02 Ksb Aktiengesellschaft Centrifugal pump impeller with a low specific speed of rotation
US5106263A (en) * 1989-09-22 1992-04-21 Jidosha Denki Kogyo K.K. Centrifugal pump with high efficiency impeller
US5451139A (en) * 1992-01-24 1995-09-19 Ebara Corporation Self priming centrifugal
US5540550A (en) * 1994-01-21 1996-07-30 Nikkiso Co., Ltd. Solid impeller for centrifugal pumps
US6779965B2 (en) * 2002-04-26 2004-08-24 Schlumberger Technology Corporation Integrated axial flow pump
US20040062647A1 (en) * 2002-09-26 2004-04-01 Garrett Norman H. Roto-dynamic fluidic systems

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20120011857A1 (en) * 2009-03-24 2012-01-19 Concepts Eti, Inc. High-Flow-Capacity Centrifugal Hydrogen Gas Compression Systems, Methods and Components Therefor
US9316228B2 (en) * 2009-03-24 2016-04-19 Concepts Nrec, Llc High-flow-capacity centrifugal hydrogen gas compression systems, methods and components therefor
US20150168342A1 (en) * 2011-02-15 2015-06-18 Michael A. Silveri Amperometric Sensor System
US9897563B2 (en) * 2011-02-15 2018-02-20 Michael A. Silveri Amperometric sensor system
US10481117B2 (en) * 2011-02-15 2019-11-19 Halogen Systems, Inc. Amperometric sensor system
US9568921B2 (en) 2012-11-15 2017-02-14 Abb Technology Oy Method for approximating a static head of a fluid transfer system
CN112253481A (zh) * 2019-10-25 2021-01-22 李亨馥 高性能卫生泵

Also Published As

Publication number Publication date
TW200916660A (en) 2009-04-16
ZA200905469B (en) 2010-05-26
EP2142804A1 (de) 2010-01-13
JP2010525223A (ja) 2010-07-22
DE102007020218A1 (de) 2008-10-30
WO2008131846A1 (de) 2008-11-06
AU2008243437A1 (en) 2008-11-06
CN101680456A (zh) 2010-03-24

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AS Assignment

Owner name: KSB AKTIENGESELLSCHAFT,GERMANY

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:BINDER, AXEL;JAEGER, CHRISTOPH;KELLER, CHRISTOPH;SIGNING DATES FROM 20091119 TO 20091205;REEL/FRAME:024088/0283

STCB Information on status: application discontinuation

Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION