EP1329638A1 - Pompe centrifuge à entrainement magnétique - Google Patents

Pompe centrifuge à entrainement magnétique Download PDF

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Publication number
EP1329638A1
EP1329638A1 EP02001323A EP02001323A EP1329638A1 EP 1329638 A1 EP1329638 A1 EP 1329638A1 EP 02001323 A EP02001323 A EP 02001323A EP 02001323 A EP02001323 A EP 02001323A EP 1329638 A1 EP1329638 A1 EP 1329638A1
Authority
EP
European Patent Office
Prior art keywords
bearing
pump
centrifugal pump
metal sleeve
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.)
Withdrawn
Application number
EP02001323A
Other languages
German (de)
English (en)
Inventor
Peter Wirz
Thomas Folsche
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.)
CP Pumpen AG
Original Assignee
CP Pumpen 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 CP Pumpen AG filed Critical CP Pumpen AG
Priority to EP02001323A priority Critical patent/EP1329638A1/fr
Publication of EP1329638A1 publication Critical patent/EP1329638A1/fr
Withdrawn legal-status Critical Current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
    • F04D29/049—Roller 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
    • 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
    • F04D13/025—Details of the can separating the pump and drive area
    • 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
    • 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
    • F04D13/027—Details of the magnetic circuit
    • 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
    • F04D29/0465—Ceramic bearing designs

Definitions

  • Such a centrifugal pump is, for example, from EP 0171515 known, in which the pump chamber with in a stationary impeller with a floating bearing through a statically sealing canned pot from the engine compartment is separated.
  • the drive motor is with a Permanent magnet connected inner rotor, which close to the wall of the canned pot on the engine compartment side is arranged.
  • the pump impeller is in turn with a external rotor provided with permanent magnets, which is close to the pump-side wall of the Canned pot is arranged. So that becomes a non - contact transmission of the rotary movement of the Drive motor realized on the pump impeller, at which caused none by shaft seals Tightness problems can occur.
  • Such pumps are used especially for fluid media used, which an optimal tightness resp. avoidance require leaks, and where no moving respectively.
  • dynamic seals are approved, such as for example with aggressive or toxic media.
  • these are usually horizontal Pump impeller axis arranged, being in the lower region of the Pump room separate, additional drainage connection must be provided.
  • This emptying nozzle must now but can also be sealed again, with these Places so-called dead spaces can occur in which Remains of the medium to be conveyed remain, i.e. one complete emptying cannot be achieved.
  • Such a pump is now known from EP 99 114 038, which essentially increases the formation of dead spaces can prevent. This is done by using a Plain bearing as the only bearing of the pump impeller reached. But it has now been shown that under certain Conditions there is a risk that the plain bearing is damaged. This is particularly the case with Pumping media with a low boiling point or low viscosity or media with bad Lubricating behavior. There is also the risk of Damage to the plain bearing in the event of incorrect operation, especially with a dry run in the case of Sterilize the pump or when the pump is emptied or if the pump is not within the permissible map is operated.
  • the object of the present invention was now that Fix the disadvantages described and a pump too create which are particularly suitable for use for the sterile process engineering.
  • this object is achieved by a pump the characterizing features of claim 1 solved.
  • Such a pump designed according to the invention is suitable is advantageous according to claim 13 for use in the fluid process engineering and in particular in the field of sterile process engineering.
  • Figure 1 shows the longitudinal section through an inventive Centrifugal pump with drive housing 1, a pump housing 2 and a suction flange attached to it, respectively.
  • -Nipple 3 In the drive housing 1 is on a flywheel 4 Permanent magnet rotor 5 arranged. Between the Drive housing 1 and the pump housing 2 is a Canned can 6 arranged, which only over his Pot edge 6 'with the drive housing 1 resp. the Pump housing 2 is connected and the drive chamber 1 'from Pump room 2 'separates statically sealing.
  • the flywheel 4 is on a shaft 7 with one in the figure not shown drive motor, for example a Electric motor, arranged.
  • a pump impeller 8 is arranged in the pump chamber 2 ', which, for example, directly in the pump impeller body Integrated permanent magnets 9, which one Form the outer permanent magnet rotor.
  • the two Permanent magnet rotors 5 and 9 are mutually spaced opposite, through the wall of the Canned pot 6 separately, concentric to the pump axis 10 arranged.
  • pump blades are formed, which the medium in the outer area of the pump room 2 'convey and via a pump outlet opening 11 dissipate.
  • the pump impeller 8 with the bearing unit consisting of preferably a lower deep groove ball bearing 13 and one upper deep groove ball bearing 14, a spacer sleeve 15 and an outer metal sleeve 16, for example a clamping screw 17 with the pump bearing bracket 12 screwed.
  • the pump bearing bracket 12 is with the Pump housing 2 firmly connected and his nose opens into the Intake space 3 'of intake 3.
  • the storage of the pump impeller 8 on the Pump bearing bracket 12 is thus under according to the invention Use of ceramic roller bearings, preferably from ceramic deep groove ball bearings 13, 14, realized.
  • the outer metal sleeve 16, which is preferably thin-walled is formed, is on the outer rings of the roller bearings 13, 14 shrunk.
  • the metal sleeve 16 is preferably made made of a material with a high yield strength, good Heat resistance, good corrosion resistance and preferably a thermal coefficient of thermal expansion, which in the range of the coefficient of thermal expansion Spacer sleeve 15 is located.
  • the shrinking process resp. the Dimensions of the metal sleeve 16 are designed such that it is at least partially plastically deformed, is preferably completely plastically deformed.
  • this metal sleeve 16 is on the outer rings of the two Deep groove ball bearings 13, 14 a favorable stress distribution achieved.
  • the wall thickness of the metal sleeve 16 can advantageously take advantage of the maximum allowable Strength values, i.e. the defined plastic Deformation required for sealing between metal sleeve 16 and the outer rings of the deep groove ball bearings 13, 14 necessary Pressing set or be limited to one Minimum radial clearance for deep groove ball bearings 13, 14 too achieve.
  • the pump impeller 8 provided with the bearing unit can then preferably via the clamping screw 17 and statically sealed to the bellhousing 12 become.
  • the sealing lips 15 'of the spacer sleeve 15 are designed that about the clamping force of the clamping screw 17 required seal between the spacer sleeve 15 and the inner ring of the deep groove ball bearings 13, 14 is reached and also the reduction of the axial clearance of the deep groove ball bearings 13, 14, resulting from the shrinking of the metal sleeve 16, is compensated. Furthermore, the resilience of the Tension screw 17 sufficient for the necessary seal between the sealing edge 12 'of the pump bearing bracket 12 and the inner ring of the lower deep groove ball bearing 13 and between the sealing edge 17 'at the head of the clamping screw 17 and the inner ring of the upper deep groove ball bearing 14 to reach.
  • the storage unit according to the invention is now very advantageous compact, has no dead spaces and has a lot good response Airflow conditions for the Cleaning process.
  • the ceramic ones offer great advantages Rolling bearings also when dry running occurs.
  • the pump presented here is suitable due to the simple and compact design and avoidance of Dead spaces and crevices especially for extreme applications in the field of sterile process engineering, but can naturally also for other areas of application be used.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Ceramic Engineering (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
EP02001323A 2002-01-18 2002-01-18 Pompe centrifuge à entrainement magnétique Withdrawn EP1329638A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP02001323A EP1329638A1 (fr) 2002-01-18 2002-01-18 Pompe centrifuge à entrainement magnétique

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP02001323A EP1329638A1 (fr) 2002-01-18 2002-01-18 Pompe centrifuge à entrainement magnétique

Publications (1)

Publication Number Publication Date
EP1329638A1 true EP1329638A1 (fr) 2003-07-23

Family

ID=8185303

Family Applications (1)

Application Number Title Priority Date Filing Date
EP02001323A Withdrawn EP1329638A1 (fr) 2002-01-18 2002-01-18 Pompe centrifuge à entrainement magnétique

Country Status (1)

Country Link
EP (1) EP1329638A1 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2008101698A1 (fr) * 2007-02-22 2008-08-28 Renner Gmbh Pompe centrifuge à entraînement magnétique pour des milieux corrosifs
EP2199616A2 (fr) 2008-12-19 2010-06-23 Bühler Motor GmbH Pompe centrifuge avec arbre fixe
CN102966557A (zh) * 2012-11-07 2013-03-13 无锡惠山泵业有限公司 清水泵
WO2016193002A1 (fr) * 2015-06-05 2016-12-08 Danfoss Commercial Compressors Compresseur de réfrigération centrifuge

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3938914A (en) * 1967-11-01 1976-02-17 March Manufacturing Company Pump impeller and coupling magnet structures
EP0171515A1 (fr) * 1984-07-16 1986-02-19 CP Pumpen AG Pompe centrifuge avec chapeau tubulaire d'isolation de l'entrefer
US4871301A (en) * 1988-02-29 1989-10-03 Ingersoll-Rand Company Centrifugal pump bearing arrangement
EP0982499A1 (fr) * 1998-08-21 2000-03-01 CP Pumpen AG Pompe centrifuge à entrainement magnétique

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3938914A (en) * 1967-11-01 1976-02-17 March Manufacturing Company Pump impeller and coupling magnet structures
EP0171515A1 (fr) * 1984-07-16 1986-02-19 CP Pumpen AG Pompe centrifuge avec chapeau tubulaire d'isolation de l'entrefer
US4871301A (en) * 1988-02-29 1989-10-03 Ingersoll-Rand Company Centrifugal pump bearing arrangement
EP0982499A1 (fr) * 1998-08-21 2000-03-01 CP Pumpen AG Pompe centrifuge à entrainement magnétique

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2008101698A1 (fr) * 2007-02-22 2008-08-28 Renner Gmbh Pompe centrifuge à entraînement magnétique pour des milieux corrosifs
EP2199616A2 (fr) 2008-12-19 2010-06-23 Bühler Motor GmbH Pompe centrifuge avec arbre fixe
EP2199616A3 (fr) * 2008-12-19 2012-07-11 Bühler Motor GmbH Pompe centrifuge avec arbre fixe
US8303268B2 (en) 2008-12-19 2012-11-06 Bühler Motor GmbH Rotary pump with a fixed shaft
DE102008064099B4 (de) * 2008-12-19 2016-05-04 Bühler Motor GmbH Kreiselpumpe mit einer feststehenden Achse
CN102966557A (zh) * 2012-11-07 2013-03-13 无锡惠山泵业有限公司 清水泵
WO2016193002A1 (fr) * 2015-06-05 2016-12-08 Danfoss Commercial Compressors Compresseur de réfrigération centrifuge
FR3037110A1 (fr) * 2015-06-05 2016-12-09 Danfoss Commercial Compressors

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