EP0744551A1 - Pompe centrifuge pour le transport de fluides chauds - Google Patents

Pompe centrifuge pour le transport de fluides chauds Download PDF

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Publication number
EP0744551A1
EP0744551A1 EP96106606A EP96106606A EP0744551A1 EP 0744551 A1 EP0744551 A1 EP 0744551A1 EP 96106606 A EP96106606 A EP 96106606A EP 96106606 A EP96106606 A EP 96106606A EP 0744551 A1 EP0744551 A1 EP 0744551A1
Authority
EP
European Patent Office
Prior art keywords
sealing
pump
mechanical seal
medium
compensation device
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.)
Granted
Application number
EP96106606A
Other languages
German (de)
English (en)
Other versions
EP0744551B1 (fr
Inventor
Jörg Urban
Waldemar Schwartz
Hans-Dieter Sturm
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
Publication of EP0744551A1 publication Critical patent/EP0744551A1/fr
Application granted granted Critical
Publication of EP0744551B1 publication Critical patent/EP0744551B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • F04D29/08—Sealings
    • F04D29/10—Shaft sealings
    • F04D29/106—Shaft sealings especially adapted for liquid pumps
    • F04D29/108—Shaft sealings especially adapted for liquid pumps the sealing fluid being other than the working liquid or being the working liquid treated
    • 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
    • F04D29/08—Sealings
    • F04D29/10—Shaft sealings
    • F04D29/12—Shaft sealings using sealing-rings
    • F04D29/126—Shaft sealings using sealing-rings especially adapted for liquid pumps
    • F04D29/128—Shaft sealings using sealing-rings especially adapted for liquid pumps with special means for adducting cooling or sealing fluid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
    • F05C2225/00—Synthetic polymers, e.g. plastics; Rubber

Definitions

  • the invention relates to a seal arrangement for a centrifugal pump for conveying hot media, consisting of at least one mechanical seal arranged in the area of a shaft bushing, a cooling circuit for cooling the mechanical seal, a partial flow of the conveying medium being usable as a cooling medium of the mechanical seal.
  • a multi-stage pump construction which is equipped with external bearing housings.
  • the bearing housings are preceded by mechanical seals located inside the pump that are exposed to the medium to be pumped.
  • the mechanical seals are preceded by throttling sections, which are used to reduce the pressure.
  • Return lines are arranged downstream in the direction of flow, with which the conveyed medium is returned to the suction nozzle.
  • a shaft seal for centrifugal pumps is known, which is arranged in the area of the shaft end and at the housing outlet.
  • the shaft seal consists of a hydrodynamic mechanical seal arranged on the atmosphere side and a further seal arranged on the pump side, with a seal located between the two seals Sealing chamber a circular flow is used for cooling and the removal of dirt particles.
  • the pump-side seal is designed as a hydrodynamic mechanical seal, which is bridged by a bypass arranged in the sealing chamber and connecting it to the inside of the pump, which serves for targeted leakage. With the help of this measure, an external cooling device is to be saved and the life of the seal is to be improved.
  • the sealing chamber itself is acted upon by the pressure medium of the centrifugal pump with the pumped medium in order to ensure the pressure necessary for the mechanical seal to function.
  • This pressure is discharged into the interior of the pump via the second mechanical seal with the help of a targeted leak.
  • the second mechanical seal thus acts as a throttle for reducing pressure.
  • their use increases the manufacturing costs of the entire pump unit.
  • the invention has for its object to realize a safe and inexpensive cooling of a mechanical seal for centrifugal pumps with an operation up to 160 ° C medium temperature.
  • This object is achieved with the features of claim 1.
  • a cooling air flow generated by the drive motor can be used in addition to others.
  • the medium circulating in the cooling circuit is separated from the rest of the medium by the sealing element, so that mixing between these areas is prevented in normal operation.
  • the pressure equalization caused between the sealing space and the pump interior relieves the sealing element located in between in the simplest way.
  • the pump interior includes all spaces that are arranged in front of the mechanical seal space.
  • the sealing element can be designed as a simple, touching sealing ring. Its material properties are selected so that it is resistant to the prevailing temperatures.
  • the pressure equalization with the help of a simple pressure relief bore does not require any special manufacturing measures. A sealing lip of the sealing element is therefore not exposed to any stress, so that special treatment of a pump shaft or a shaft protection sleeve located thereon is unnecessary.
  • the promotional effect within the cooling circuit the mechanical seal itself or auxiliary devices connected to it are generated. The cooling circuit removes the heat that is transferred from the pump material to the cooling medium during operation.
  • thermosiphon circuit is formed within the cooling circuit, which ensures sufficient cooling of the mechanical seal even when a centrifugal pump is in the ready state in the ready state.
  • the sealing ring which is to a certain extent upstream of the mechanical seal, prevents heat exchange with the hot pumping medium in the simplest way in normal operation.
  • a hot medium is only fed into the cooling medium if the pressure inside the cooling circuit should drop due to a seal leak. Only in such cases is lost cooling medium replaced by hot, flowing medium.
  • a pressure housing 1 with the last impeller 2 located therein is shown.
  • This impeller 2 is followed by an axial thrust compensation device 3, from which a return line 4 leads to the suction port of the centrifugal pump, not shown here.
  • the axial thrust compensation device can also be dispensed with if the structural design of the pump provides compensation in a different way, e.g. B. by opposing arrangement.
  • the axial thrust compensation device is followed by a sealing element 5, which separates the space 6 containing the axial thrust compensation device 3 from an actual seal space 8 containing a mechanical seal 7.
  • the seal chamber 8 has a drain line 9 through which heated medium flows outwards, one - not here shown - cooler passes and is introduced as a cooled medium through the line 10 in the region of an opening 11 in the seal chamber 8 of the seal housing 12.
  • the contacting sealing element (5) designed here as a sealing ring rests on the rotating part of the pump, in the exemplary embodiment shown on a shaft protection sleeve (14) which is pushed over a pump shaft (22).
  • the sealing element or the sealing ring (5) can also bear directly on a pump shaft (22) or another rotating pump part. It effectively prevents an exchange between the hot medium and the lower temperature cooling medium. At most, in situations in which cooling medium has to be replaced by medium through leakage in the area of the mechanical seal, there is an inflow of medium.
  • the pumped medium flows from the area of the last impeller (2) through a bearing gap (13) to the - if applicable - axial thrust compensation device (3). From their space (6) the hot medium flows in front of the sealing ring (5) via the gaps (15, 16, 17) into a collecting space (18), from where it is low through a return line (4) to the suction nozzle or a point Pressure of the centrifugal pump is supplied.
  • a pressure compensation device (19) is arranged between the collecting space (18) for the conveyed medium and the sealing space (8).
  • This is designed as a simple through hole and, as shown, can also penetrate the sealing element (5) in a recess (20).
  • a non-contact sealing element for example in the form of a labyrinth seal, would be unsuitable, since its sealing effect is insufficient and excessive heat transfer would take place due to the hot pumping medium flowing through.
  • the sealing housing is therefore heated exclusively by heat transfer to the metallic parts.
  • the circled sealing element in Fig. 1 is shown in Fig. 2 in an enlarged view.
  • the shape of the pressure compensation device selected here has the additional advantage that it simultaneously forms an anti-rotation device for the sealing element.
  • the embodiment of a pressure compensation device (19) selected here consists of a tubular component which penetrates the wall surface of the collecting space (18). It extends with part of its length into a recess (20) in the sealing element (5), which is thus held in its position to prevent rotation. With a U-shaped design, the recess (20) allows the sealing element (5) to be simply pushed into the installation position during installation.
  • the pressure compensation device (19) can be designed in a simple form as a dowel pin. When arranged at a location other than the one shown, the axial overall length increases slightly, but the system as such is still functional.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
EP96106606A 1995-05-20 1996-04-26 Pompe centrifuge pour le transport de fluides chauds Expired - Lifetime EP0744551B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19518564 1995-05-20
DE19518564A DE19518564A1 (de) 1995-05-20 1995-05-20 Kreiselpumpe zur Förderung heißer Medien

Publications (2)

Publication Number Publication Date
EP0744551A1 true EP0744551A1 (fr) 1996-11-27
EP0744551B1 EP0744551B1 (fr) 2000-07-05

Family

ID=7762434

Family Applications (1)

Application Number Title Priority Date Filing Date
EP96106606A Expired - Lifetime EP0744551B1 (fr) 1995-05-20 1996-04-26 Pompe centrifuge pour le transport de fluides chauds

Country Status (5)

Country Link
US (1) US5795129A (fr)
EP (1) EP0744551B1 (fr)
AT (1) ATE194412T1 (fr)
DE (2) DE19518564A1 (fr)
DK (1) DK0744551T3 (fr)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE29704389U1 (de) * 1997-03-11 1997-05-07 Burgmann Dichtungswerk Feodor Leckagerückführanordnung bei einer Dichtungseinrichtung
EP1087144B1 (fr) * 1999-09-23 2005-11-30 Cryomec AG Joint tandem tournant pour pompes cryogéniques
DE502006004968D1 (de) * 2006-01-12 2009-11-12 Sulzer Pumpen Ag Strömungsmaschine für ein Fluid mit einem radialen Dichtspalt
MX2011002665A (es) 2008-09-10 2011-07-28 Pentair Pump Group Inc Bomba centrifuga de multiples etapas, de alta eficiencia y metodo para ensamblado.
DE102009023907A1 (de) 2009-06-04 2010-12-09 Ksb Aktiengesellschaft Dichtungssystem für Kreiselpumpen

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3090320A (en) * 1960-12-07 1963-05-21 Durametallic Corp Seals for stuffing boxes and the like permitting flushing thereof
FR2188727A5 (fr) * 1972-06-09 1974-01-18 Burgmann Dichtungswerk Feodor
US3999882A (en) * 1975-03-17 1976-12-28 Dresser Industries, Inc. Flushing and cooling system for shaft seals and pumps
FR2388148A1 (fr) * 1977-04-22 1978-11-17 Dresser Ind Circuit de balayage et de refroidissement perfectionne pour pompes
JPS59119099A (ja) * 1982-12-24 1984-07-10 Hitachi Ltd 高温・高圧流体用回転ポンプの軸封装置
DE8601166U1 (de) * 1986-01-18 1986-02-27 Sihi Gmbh & Co Kg, 2210 Itzehoe Pumpe zur Förderung von Heißwasser
EP0588259A1 (fr) * 1992-09-14 1994-03-23 KSB Aktiengesellschaft Recyclage de l'eau de compensation de la poussée axiale

Family Cites Families (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3825270A (en) * 1972-05-09 1974-07-23 Standun Wiper seal for apparatus such as metallic can body formers
US4053163A (en) * 1974-12-26 1977-10-11 George Vegella Seal construction
DE2630513C2 (de) * 1976-07-07 1985-11-28 Allweiler Ag, 7760 Radolfzell Kühleinrichtung für ein Pumpenaggregat
US4121839A (en) * 1976-08-18 1978-10-24 Mitsui Toatsu Chemicals, Inc. Sealing system for use in composite multi-stage pump
DE2645755A1 (de) * 1976-10-09 1978-04-13 Klein Schanzlin & Becker Ag Wellendichtung
DE2925244C2 (de) * 1979-06-22 1982-09-30 Howaldtswerke-Deutsche Werft Ag Hamburg Und Kiel, 2300 Kiel Abdichtungsanordnung für Stevenrohranlagen
DE3324468A1 (de) * 1983-07-07 1985-01-17 Krull, Gerhard, 4803 Steinhagen Abgedichtetes waelzlager, insbesondere fuer wasserpumpen in kraftfahrzeugen
DE3342297A1 (de) * 1983-11-23 1985-06-05 Howaldtswerke-Deutsche Werft Ag Hamburg Und Kiel, 2300 Kiel Vorrichtung zum abdichten eines oelgeschmierten lagers in groesserer wassertiefe
DE3804183C2 (de) * 1988-02-11 1994-11-24 Klein Schanzlin & Becker Ag Wellendichtung für Kreiselpumpen
GB8901656D0 (en) * 1989-01-26 1989-03-15 Flexibox Ltd Shaft seal
US5180297A (en) * 1991-03-22 1993-01-19 The Gorman-Rupp Company Fluid transfer pump with shaft seal structure
DE9318143U1 (de) * 1993-11-26 1994-01-27 Abel Gmbh & Co Abgedichteter Wellenaustritt aus einem Pumpengehäuse

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3090320A (en) * 1960-12-07 1963-05-21 Durametallic Corp Seals for stuffing boxes and the like permitting flushing thereof
FR2188727A5 (fr) * 1972-06-09 1974-01-18 Burgmann Dichtungswerk Feodor
US3999882A (en) * 1975-03-17 1976-12-28 Dresser Industries, Inc. Flushing and cooling system for shaft seals and pumps
FR2388148A1 (fr) * 1977-04-22 1978-11-17 Dresser Ind Circuit de balayage et de refroidissement perfectionne pour pompes
JPS59119099A (ja) * 1982-12-24 1984-07-10 Hitachi Ltd 高温・高圧流体用回転ポンプの軸封装置
DE8601166U1 (de) * 1986-01-18 1986-02-27 Sihi Gmbh & Co Kg, 2210 Itzehoe Pumpe zur Förderung von Heißwasser
EP0588259A1 (fr) * 1992-09-14 1994-03-23 KSB Aktiengesellschaft Recyclage de l'eau de compensation de la poussée axiale

Non-Patent Citations (2)

* Cited by examiner, † Cited by third party
Title
EHRHARD MAYER: "axiale gleitdichtungen", VDI-VERLAG GMBH, DUSSELDORF, XP002008593 *
PATENT ABSTRACTS OF JAPAN vol. 008, no. 240 (M - 336) 6 November 1984 (1984-11-06) *

Also Published As

Publication number Publication date
DK0744551T3 (da) 2000-11-06
EP0744551B1 (fr) 2000-07-05
DE59605536D1 (de) 2000-08-10
US5795129A (en) 1998-08-18
DE19518564A1 (de) 1996-11-21
ATE194412T1 (de) 2000-07-15

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