US20080213087A1 - Pump for Liquids Under Positive Pressure - Google Patents

Pump for Liquids Under Positive Pressure Download PDF

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Publication number
US20080213087A1
US20080213087A1 US11/720,326 US72032605A US2008213087A1 US 20080213087 A1 US20080213087 A1 US 20080213087A1 US 72032605 A US72032605 A US 72032605A US 2008213087 A1 US2008213087 A1 US 2008213087A1
Authority
US
United States
Prior art keywords
shaft
impeller
pump
support element
pump according
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Abandoned
Application number
US11/720,326
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English (en)
Inventor
Peter Wagner
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.)
Brinkmann Pumpen KH Brinkmann GmbH and Co KG
Original Assignee
Brinkmann Pumpen KH Brinkmann GmbH and Co KG
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 Brinkmann Pumpen KH Brinkmann GmbH and Co KG filed Critical Brinkmann Pumpen KH Brinkmann GmbH and Co KG
Assigned to BRINKMANN PUMPEN K.H. BRINKMANN GMBH & CO. KG reassignment BRINKMANN PUMPEN K.H. BRINKMANN GMBH & CO. KG ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: WAGNER, PETER
Publication of US20080213087A1 publication Critical patent/US20080213087A1/en
Abandoned legal-status Critical Current

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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
    • F04D29/00—Details, component parts, or accessories
    • F04D29/04—Shafts or bearings, or assemblies thereof
    • F04D29/046—Bearings
    • F04D29/047—Bearings hydrostatic; hydrodynamic
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D13/00—Pumping installations or systems
    • F04D13/02—Units comprising pumps and their driving means
    • F04D13/021—Units comprising pumps and their driving means containing a coupling
    • F04D13/024—Units comprising pumps and their driving means containing a coupling a magnetic coupling
    • F04D13/026—Details of the bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/04—Shafts or bearings, or assemblies thereof
    • F04D29/041—Axial thrust balancing
    • F04D29/0413—Axial thrust balancing hydrostatic; hydrodynamic thrust bearings

Definitions

  • the invention relates to a pump for liquids under positive pressure, comprising a pump chamber which accommodates an impeller.
  • a high pressure When pumping a liquid at a temperature above its boiling point, a high pressure must be maintained in order to prevent the liquid from evaporating.
  • a pump For example, for hot water having a temperature of 120° C., a pump must operate at a pressure of, for example, 0.25 MPa (2.5 bar), without any pressure losses. It can be assumed that, for an increase in temperature of 10° C., the pressure must be increased by approximately 0.1 MPa.
  • this object is achieved by the feature that the impeller is axially biased against a non-rotating support element which determines the axial position of the impeller. Since the axial position of the impeller is determined by the support element, the dimensions of the pump chamber and the impeller can be adapted one another with very high precision, so that a very small gap between the impeller and the walls of the pump chamber can be maintained.
  • the pump is suitable for pumping hot water at high temperatures and at correspondingly high pressures.
  • the impeller is fixed on a shaft which is axially biased against the support element.
  • a sliding rotary motion between the shaft and the support element occurs on a small radius, so that the frictional resistance is reduced.
  • the shaft and the support element are preferably made of a ceramic material.
  • the shaft is supported in at least one radial slide bearing. Accordingly, the radial position of the impeller can also be defined with high precision.
  • the shaft and the slide bearing are preferably made of a ceramic material.
  • the shaft is displaceably supported in the bearing, so that it is possible to axially bias the shaft and the impeller, respectively, against the support element.
  • the support element and the at least one slide bearing are flushed with the liquid to be pumped, when the pump is operating.
  • a flush passage passing through a wall of the pump chamber for flushing the at least one slide bearing connects a pressure-side region of the pump chamber with a region situated beyond the slide bearing. In this way, the slide bearing can reliably be flushed with the liquid being pumped.
  • a flush passage for flushing the at least one slide bearing is formed by a passage passing axially in the shaft. This passage may be provided in addition to the flush passage formed in the wall of the pump chamber.
  • the pump may be operated not only with a horizontal axis of rotation of the impeller but also in a suspended position, i.e. with a vertical axis of rotation of the impeller.
  • a radial play between the impeller and the pump chamber is not larger than 1/10 mm. This corresponds to an average distance between the impeller and a wall of the pump chamber of 5/100 mm. It is particularly preferred that the play amounts to not more than 5/100 mm, corresponding to an average spacing of 0.025 mm.
  • an axial spacing between the impeller and the pump chamber on both sides of the impeller is not larger than 1/10 mm. More preferably, this spacing amounts to not more than 5/100 mm, particularly preferred is a spacing of 3/100 mm or less.
  • the shaft is coupled to a drive shaft by a magnet coupling, wherein a first coupling member of the magnet coupling is connected to the shaft, a second coupling member of the magnet coupling is connected to the drive shaft, and a wall, which seals the drive portion of the pump against a portion accommodating the shaft and the pump chamber of the pump, passes through a gap between the first and second coupling members.
  • the pump may operate for example in a pressure range from 0.6 to 0.65 MPa, so that hot water at a temperature of 160° C., for example, may be pumped. Such temperatures are not allowable in conjunction with conventional rubber seals, for example.
  • the first and second coupling members are so arranged relative to one another that the magnet coupling urges the shaft axially against the support element.
  • the magnet coupling fulfills two functions. On the one hand, it permits to seal the portion of the pump, which contains the liquid to be pumped, by a closed wall, so that no seals need to be employed at the rotating parts. On the other hand, it assures that the impeller and the shaft, respectively, are axially biased against the support element.
  • the shaft is axially biased against the support element by a compression spring.
  • the compression spring may also be used when a magnet coupling is provided.
  • FIG. 1 is a partial section of a first embodiment of a pump having a magnet coupling
  • FIG. 2 is a partial section of a second embodiment of a pump having a slip-ring seal and a compression spring.
  • the pump shown in FIG. 1 has an essentially cylindrical casing 10 to which an intermediate member 12 is flanged at the lower end thereof, and a head member 14 is flanged to the intermediate member. These members are screw-tightened to the casing 10 by means of bolts 16 which pass through the head member 14 .
  • a pump chamber 18 is formed, which extends between the intermediate member 12 and the head member 14 in the shape of an interrupted ring and connects an intake passage of an intake pipe, which has not been shown, to an outlet passage 20 of an outlet pipe 22 .
  • the outlet passage 22 formed in the intermediate member 12 is positioned behind the plane of the drawing, whereas the intake passage, which has not been shown, is formed in the head member 14 and is situated in front of the plane of the drawing.
  • the pump chamber 18 accommodates an impeller 24 having a disk-shaped central portion 26 and impeller blades 28 , 30 which are arranged above and below the central portion 26 and each extend radially into an outer region of the impeller 24 .
  • the blades 28 arranged above the central portion 26 i.e. on the side of the outlet passage 20 , are slightly displaced rearwardly in the direction of rotation of the impeller 24 relative to the blades 30 provided below the central portion 26 .
  • the blades 28 extend axially upwardly up to an upper face 32 of the impeller 24 .
  • the blades 30 extend axially downwardly up to a lower face 34 of the impeller.
  • the upper face 32 approaches a wall formed by the intermediate member 12 and forms therewith a gap of, for example, 2/100 mm
  • the lower face 34 approaches a wall formed by the head member 14 and forms therewith a gap of, for example, 3/100 mm.
  • the blades 28 , 30 and the central portion 26 of the impeller 24 extend radially outwardly up to a straight outer periphery 36 of the impeller 34 .
  • the outer periphery 36 in the range between the end of the pump chamber 18 at the outlet passage 20 and the start of the pump chamber 18 at the intake passage, has a lateral spacing of only 0.025 mm from a wall that is formed for example by the head member 14 . Thanks to the small lateral and axial spacings between the impeller 24 and the surrounding walls, the pump is capable of maintaining a very high pressure.
  • the impeller 24 is fixedly mounted by means of a sleeve-type projection 38 and by means of tolerance rings or corrugated rings 40 on a shaft 42 that is made of ceramic material. Below the impeller 24 , the shaft 42 is supported in a slide bearing 44 that is fixed in the head member 14 with a corrugated ring 46 .
  • the slide bearing 44 is made of a ceramic material, e.g. silicon carbide.
  • the shaft 42 is slidingly supported on a ceramic support element 48 that is formed for example by a perforated disk of tungsten carbide and is fixed to the head member 14 with a bolt 50 .
  • the shaft 42 is guided in another slide bearing 52 which is fixed at the intermediate member 12 with a corrugated ring 54 .
  • the shaft 42 is slidingly guided in the slide bearings 44 , 52 .
  • a first coupling member 56 of a magnet coupling is fixed to the top end of the shaft 42 with a corrugated ring 58 .
  • the first coupling member 56 extends in an annular shape around the end of the shaft 42 and is surrounded with a spacing by an annular flange 60 of a second coupling member 62 of the magnet coupling.
  • the second coupling member 62 is fixed at the lower end of a drive shaft 64 that is supported at the casing 10 with a fixed bearing 66 .
  • the drive shaft 64 is driven by a motor of the pump.
  • a separating can 68 is arranged in a pot-shaped hollow space formed between the coupling members 56 and 62 , the separating can having a very small wall thickness in the region of an annular gap 70 formed between the first coupling member 56 and the flange 60 .
  • the separating can 68 forms a wall made of a non-magnetic material, e.g. of VA steel. It is sealed against the intermediate member 12 with a sealing ring 72 , and the intermediate member 12 is again sealed against the head member 14 with a sealing ring 74 . In this way, a closed hollow space is formed, which encompasses the pump chamber 18 and is open only at the intake passage and the outlet passage 20 .
  • magnet elements 76 arranged in the first coupling member 56 are opposed to magnet elements 78 that are arranged in the flange 60 . They magnetically transmit a drive torque from the drive shaft 64 onto the shaft 42 and hence onto the impeller 24 .
  • the magnet elements 76 and 78 are axially offset relative to one another in such a way that they exert an axial force onto the shaft 42 , which urges and biases the shaft 42 against the support element 48 .
  • the axial position of the impeller 24 relative to the head member 14 and thus also relative to the intermediate member 12 is defined exactly, so that, in spite of the very small axial spacings, no contact will occur between the impeller 24 and these members. For this reason, the pump operates with very little wear.
  • a flush passage 80 starts in the vicinity of the outlet-side end of the pump chamber 18 , passes upwardly through the intermediate member 12 and opens in the region of the coupling member 56 .
  • the flush passage 80 is formed by a straight bore which is tapered at the lower end, so as to limit the flow into the flush passage.
  • One purpose of the liquid that is driven upwardly through the flush passage 80 is to flush the slide bearing 52 . Moreover, this liquid is forwarded through a passage 82 in the form of an axial through-bore of the shaft 42 to the lower end of the shaft, where the liquid exits laterally through grooves 84 , that have been indicated in chain lines, and serves to flush the slide bearing 44 .
  • the embodiment of the pump shown in FIG. 2 differs from the one shown in FIG. 1 especially by that it has no magnet coupling. Like or similar parts are designated by like reference numerals.
  • the impeller 24 is fixed on a shaft 86 with corrugated rings 40 , the shaft 86 being supported at its lower end in the slide bearing 44 and being supported on the support element 48 like the shaft 42 in FIG. 1 .
  • the shaft 86 is reduced in diameter, passes through a bore 88 of the intermediate member 12 and is coupled to the drive shaft 64 by a tappet sleeve 90 .
  • a gap between the shaft 86 and the bore 88 is sealed by a slip-ring seal 92 at a seal face 94 .
  • the slip-ring seal 92 is pressed upwardly against the seal face 94 by a compression spring 98 the lower end of which is supported on a shoulder of the shaft 86 .
  • the compression spring 98 will at the same time urge the shaft 86 downwardly against the support element 48 .
  • the exact axial position of the impeller 24 relative to the head member 14 and the intermediate member 12 is defined, similarly as in the first embodiment.
  • the small spacings between the impeller 24 and the adjoining walls of the pump chamber 18 are made possible by the exact axial and radial positioning of the impeller 24 . Thanks to this, the pump operates with very little wear, and very high temperatures and pressures of the liquid to be pumped are possible, in spite of the use of a slip-ring seal at the rotating shaft 86 . Thus, for example, it is possible to pump hot water at a temperature in the range of 120 to 130° C.
  • a cross bore 100 is provided in the sleeve-type projection 38 and in the shaft 86 above the impeller 24 , and the cross-bore opens into a passage 102 formed by an axial bore of the shaft 86 , through which liquid for flushing the slide bearing 44 is again supplied from the upper portion of the intermediate member 12 towards the lower end of the shaft 86 , where it exits through the grooves 84 .
  • a vent and flush passage 104 extends in a height approximately below the slip-ring seal 92 from the upper portion of the head member 12 to the outlet passage 20 and passes through a web 106 formed at the outlet pipe 22 .
  • the described embodiments of the pump have the outstanding feature that the constructions of the head member 14 and of the casing 10 and the drive shaft 64 are identical, and that, in each case, the lower part of the pump comprising the intermediate member 12 , the head member 14 , the impeller 24 and the shaft 42 and 86 , respectively, can be removed for maintenance purposes. Further, this makes it possible to convert the one embodiment of the pump into the other one by exchanging the lower part of the pump.
  • the dividing line, where the exchangeable part is fitted to the upper part of the pump, is always located outside of the range of the liquid to be pumped.
US11/720,326 2004-12-04 2005-11-12 Pump for Liquids Under Positive Pressure Abandoned US20080213087A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102004058533A DE102004058533B4 (de) 2004-12-04 2004-12-04 Pumpe für Flüssigkeiten unter Überdruck
DE102004058533.4 2004-12-04
PCT/EP2005/012142 WO2006058607A1 (en) 2004-12-04 2005-11-12 Pump for liquids under positive pressure

Publications (1)

Publication Number Publication Date
US20080213087A1 true US20080213087A1 (en) 2008-09-04

Family

ID=35636668

Family Applications (1)

Application Number Title Priority Date Filing Date
US11/720,326 Abandoned US20080213087A1 (en) 2004-12-04 2005-11-12 Pump for Liquids Under Positive Pressure

Country Status (7)

Country Link
US (1) US20080213087A1 (de)
EP (1) EP1817502A1 (de)
JP (1) JP2008522093A (de)
CN (1) CN101076669A (de)
DE (1) DE102004058533B4 (de)
TW (1) TW200626804A (de)
WO (1) WO2006058607A1 (de)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20140158320A1 (en) * 2011-04-15 2014-06-12 Eirik Archer Subsea cooling apparatus, and a separately retrievable submersible pump module for a submerged heat exchanger
US20160084258A1 (en) * 2013-05-08 2016-03-24 Ksb Aktiengesellschaft Pump Arrangement Comprising a Plain Bearing Arrangement
US10330107B2 (en) 2013-05-08 2019-06-25 Ksb Aktiengesellschaft Drive rotor for a magnetically coupled pump having tolerance rings
US11555498B2 (en) * 2017-04-11 2023-01-17 Fsubsea As Magnetic coupling assemblies and pump, turbine, and compressor including the magnetic coupling assembly
CN116624435A (zh) * 2023-04-18 2023-08-22 烟台龙港泵业股份有限公司 反向冲洗的中心出液式液下泵、立式筒袋泵

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP5428042B2 (ja) * 2009-01-26 2014-02-26 アルファ株式会社 物質供給計量装置、粒子加工装置、被覆装置及び被覆システム
JP6066606B2 (ja) * 2012-07-20 2017-01-25 ミネベア株式会社 多段式渦流ポンプ

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1843504A (en) * 1927-01-05 1932-02-02 Jeffrey Mfg Co Cable reel
US3238878A (en) * 1964-03-09 1966-03-08 Micro Pump Corp Centrifugal pump with magnetic drive
US4013384A (en) * 1974-07-18 1977-03-22 Iwaki Co., Ltd. Magnetically driven centrifugal pump and means providing cooling fluid flow
US4508492A (en) * 1981-12-11 1985-04-02 Nippondenso Co., Ltd. Motor driven fuel pump
US4648808A (en) * 1984-07-16 1987-03-10 Cp Pumpen Ag Sealing shroud centrifugal pump
US5302091A (en) * 1992-03-24 1994-04-12 Sanwa Hydrotech Corp. Magnetically driven centrifugal pump

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JPS5114803A (en) * 1974-07-29 1976-02-05 Nippon Steel Corp Koroheno genryosonyuhoho
JPS58138294A (ja) 1982-02-10 1983-08-17 Ngk Insulators Ltd マグネツトポンプの軸受部冷却水供給装置
DE3639719C3 (de) * 1986-11-20 1994-02-24 Hermetic Pumpen Gmbh Spaltrohrmagnetpumpe
DE69023317T2 (de) * 1989-11-08 1996-04-25 Sanwa Tokushu Seiko Co Magnetisch angetriebene Pumpe.
JPH07310692A (ja) * 1994-05-12 1995-11-28 Aisan Ind Co Ltd 電動燃料ポンプ
JP3463356B2 (ja) * 1994-06-30 2003-11-05 株式会社デンソー ウエスコポンプ
JPH08277795A (ja) * 1995-04-05 1996-10-22 Matsushita Electric Ind Co Ltd 遠心ポンプ
DE29716110U1 (de) * 1997-09-08 1999-01-14 Speck Pumpenfabrik Walter Spec Magnetkupplungspumpe
GB9819261D0 (en) * 1998-09-03 1998-10-28 Concentric Pumps Ltd Improvements to rotary pumps

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1843504A (en) * 1927-01-05 1932-02-02 Jeffrey Mfg Co Cable reel
US3238878A (en) * 1964-03-09 1966-03-08 Micro Pump Corp Centrifugal pump with magnetic drive
US4013384A (en) * 1974-07-18 1977-03-22 Iwaki Co., Ltd. Magnetically driven centrifugal pump and means providing cooling fluid flow
US4508492A (en) * 1981-12-11 1985-04-02 Nippondenso Co., Ltd. Motor driven fuel pump
US4648808A (en) * 1984-07-16 1987-03-10 Cp Pumpen Ag Sealing shroud centrifugal pump
US5302091A (en) * 1992-03-24 1994-04-12 Sanwa Hydrotech Corp. Magnetically driven centrifugal pump

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20140158320A1 (en) * 2011-04-15 2014-06-12 Eirik Archer Subsea cooling apparatus, and a separately retrievable submersible pump module for a submerged heat exchanger
US9719698B2 (en) * 2011-04-15 2017-08-01 Kongsberg Oil & Gas Technologies As Subsea cooling apparatus, and a separately retrievable submersible pump module for a submerged heat exchanger
US20160084258A1 (en) * 2013-05-08 2016-03-24 Ksb Aktiengesellschaft Pump Arrangement Comprising a Plain Bearing Arrangement
US10253783B2 (en) * 2013-05-08 2019-04-09 Ksb Aktiengesellschaft Pump arrangement comprising a plain bearing arrangement
US10330107B2 (en) 2013-05-08 2019-06-25 Ksb Aktiengesellschaft Drive rotor for a magnetically coupled pump having tolerance rings
US11555498B2 (en) * 2017-04-11 2023-01-17 Fsubsea As Magnetic coupling assemblies and pump, turbine, and compressor including the magnetic coupling assembly
CN116624435A (zh) * 2023-04-18 2023-08-22 烟台龙港泵业股份有限公司 反向冲洗的中心出液式液下泵、立式筒袋泵

Also Published As

Publication number Publication date
DE102004058533A1 (de) 2006-06-08
DE102004058533B4 (de) 2011-04-21
TW200626804A (en) 2006-08-01
EP1817502A1 (de) 2007-08-15
JP2008522093A (ja) 2008-06-26
CN101076669A (zh) 2007-11-21
WO2006058607A1 (en) 2006-06-08

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Legal Events

Date Code Title Description
AS Assignment

Owner name: BRINKMANN PUMPEN K.H. BRINKMANN GMBH & CO. KG, GER

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:WAGNER, PETER;REEL/FRAME:019347/0268

Effective date: 20070515

STCB Information on status: application discontinuation

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