EP2438305B1 - Dichtungssystem für kreiselpumpen - Google Patents

Dichtungssystem für kreiselpumpen Download PDF

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Publication number
EP2438305B1
EP2438305B1 EP10722626.8A EP10722626A EP2438305B1 EP 2438305 B1 EP2438305 B1 EP 2438305B1 EP 10722626 A EP10722626 A EP 10722626A EP 2438305 B1 EP2438305 B1 EP 2438305B1
Authority
EP
European Patent Office
Prior art keywords
housing
seal
seal housing
projection
housing cover
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.)
Active
Application number
EP10722626.8A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP2438305A1 (de
Inventor
Bernhard Brecht
Uwe Bruhns
Frank Sehr
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 EP2438305A1 publication Critical patent/EP2438305A1/de
Application granted granted Critical
Publication of EP2438305B1 publication Critical patent/EP2438305B1/de
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • F04D29/12—Shaft sealings using sealing-rings
    • F04D29/126—Shaft sealings using sealing-rings especially adapted for liquid pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D27/00—Control, e.g. regulation, of pumps, pumping installations or pumping systems specially adapted for elastic fluids
    • F04D27/02—Surge control
    • F04D27/0207—Surge control by bleeding, bypassing or recycling fluids
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D27/00—Control, e.g. regulation, of pumps, pumping installations or pumping systems specially adapted for elastic fluids
    • F04D27/02—Surge control
    • F04D27/0207—Surge control by bleeding, bypassing or recycling fluids
    • F04D27/0215—Arrangements therefor, e.g. bleed or by-pass valves
    • 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
    • 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
    • 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
    • F04D29/0416—Axial thrust balancing balancing pistons
    • 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
    • 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
    • F04D29/5893—Cooling; Heating; Diminishing heat transfer specially adapted for liquid pumps heat insulation or conduction
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D7/00—Pumps adapted for handling specific fluids, e.g. by selection of specific materials for pumps or pump parts
    • F04D7/02—Pumps adapted for handling specific fluids, e.g. by selection of specific materials for pumps or pump parts of centrifugal type
    • F04D7/06—Pumps adapted for handling specific fluids, e.g. by selection of specific materials for pumps or pump parts of centrifugal type the fluids being hot or corrosive, e.g. liquid metals

Definitions

  • the invention relates to a centrifugal pump for conveying hot fluids, with a contacting shaft seal, a seal housing for the shaft seal and a return line for a partial flow of the conveying fluid.
  • Such a centrifugal pump is in the DE 42 30 715 A1 described, which is used as a feed pump for the promotion of hot fluids.
  • a discharge fluid exiting from the discharge device forms a partial flow of the delivery fluid.
  • This partial flow also known as discharge water, is used to cool a mechanical seal. For this purpose, it flows through the sealing space completely, thereby dissipating the frictional heat generated during operation of the mechanical seal.
  • the discharge water is then removed from the seal space via a return line connecting the seal housing to a pump stage.
  • This type of shaft seal cooling can only be used up to a certain operating temperature of the delivery fluid.
  • a centrifugal pump with a sealing system for higher operating temperatures is used in the DE 195 18 564 A1 described.
  • a further sealing element is arranged, which bears against the rotating part of the pump.
  • This sealing element consists of a high polymer plastic.
  • the sealing element shields the sealing space from the hot conveying fluid in the pump interior and at the same time ensures a pressure equalization with respect to the sealing space.
  • the discharge water is returned through a return line to the suction side of the centrifugal pump.
  • the seal housing is integrated into a cooling circuit, the cooling fluid was initially removed from the fluid flow. By a connected to the seal housing separate cooling circuit, the heat is removed from the cooling fluid.
  • conventional external cooling systems can be used.
  • the object of the present invention is to provide a multi-stage centrifugal pump in which the shaft sealing system is designed for a temperature range of the conveying fluid exceeding 160 ° C. and that it can be used for the entire temperature range of feed pumps. Furthermore, it is an object of the invention to dispense with the supply of external cooling fluids in the seal chamber and to provide a cost-effective, reliable sealing system.
  • seal housing composed of an inner part and an outer part, wherein the inner part of a different material than the outer part.
  • the rotating component may be either the shaft of the pump or a shaft sleeve pushed over the pump shaft.
  • the axial gap extends parallel to the shaft and passes around the shaft. Geometrically, this gap is a hollow cylinder.
  • the gap throttles the influx of the pump delivery fluid into the seal chamber. The narrower and the longer the gap, the less discharge water can enter the seal housing.
  • the invention is used in multi-stage centrifugal pumps, in which the centrifugal pump has a relief device for the axial thrust, the contacting shaft seal of the relief device is arranged downstream, being discharged through the return line discharge water.
  • the return line for the discharge water is an additional source of heat when conveying hot fluids, which can exert a negative influence on the shaft seal.
  • the connection for a return line for the discharge water has been arranged away from the seal housing. Thus, the heat from the return line can not be delivered directly to the seal housing.
  • the new seal housing encloses the touching seal.
  • the seal is a mechanical seal.
  • the division into a housing cover and a new seal housing a thermal decoupling of the seal chamber is achieved with respect to the hot pump housing. On the one hand, this happens because the heat conduction between the housing cover and the seal housing is minimized. On the other hand, a delivery fluid arising as discharge water is already removed from the pump housing away from the seal housing.
  • the seal housing on a projection.
  • this projects in the form of a shoulder encompassing the shaft on the inside of the seal housing.
  • the paragraph serves as a centering for the seal housing with respect to the housing closing the pump housing. Due to the surface of the projection, the heat conduction-related contact surfaces are reduced to a strength necessary measure. The aim is to make this contact surface as small as possible in order to minimize the heat conduction from the housing cover into the seal housing.
  • the housing cover also has a projection.
  • the projection of the housing cover protrudes into the seal housing.
  • the projection of the housing cover is also formed as a hollow cylinder surrounding the shaft. The seal housing is pushed onto the outer circumferential surface of the housing cover projection until the projection of the seal housing meets the housing cover.
  • the projection of the seal housing and the projection of the housing cover are force-transmitting to each other and can overlap each other.
  • the heat conduction between the parts is additionally reduced if a heat-insulating sealing element is positioned between the contact surface of the projection and the housing cover.
  • the projection can also be an individual part in the form of a thermally insulating, centering and can be arranged between the seal housing and housing cover connecting element. This results in a greater combination ability of such a seal housing with different types of pumps. Likewise, as part of a pump revision, older pumps can be retrofitted and thus upgraded for another field of application.
  • the seal housing is composed of an inner and an outer part.
  • the inner part that surrounds the contacting seal is made of a different material than the outer part. It proves to be advantageous if the inner part is designed as a sleeve which is thermally conductively and force-transmittingly connected to the outer part, for example, it may be shrunk. It is also conceivable that the outer part is provided on its inside with a protective coating, plating or the like. In this case, the coating or plating forms the inner part of the seal housing.
  • the outer part of the seal housing has a better thermal conductivity than the inner part. This allows the heat to be dissipated quickly to the outside. As low it has proven to form the outer part of the seal housing as a bronze body. But also others, good thermally conductive and resistant to the prevailing strength requirements materials are used.
  • the inner part of the seal housing is preferably made of a material which is particularly resistant to corrosion by the fluid being conveyed.
  • the inner part of the seal housing is formed by a stainless steel sleeve. This can be shrunk into the outer part, for example a bronze body.
  • the stainless steel sleeve ensures corrosion resistance.
  • the bronze body ensures that the heat from the seal chamber is sufficiently dissipated to the environment of the pump.
  • the projection of the seal housing is formed by the inner part of the seal housing. Only the projection has a direct contact with the housing cover. Since the inner part of the seal housing is made of a material with a poor thermal conductivity, for example stainless steel, in this embodiment, the heat flow, which is transferred from the hot housing cover to the cool-seal housing, reduced in size. As a result, a better thermal decoupling of the seal housing is achieved by the housing cover.
  • the housing cover is made of a material having a poor thermal conductivity. It has proved to be particularly advantageous to manufacture the housing cover made of an alloyed, chemically resistant, steel. It proves to be advantageous while a steel with the steel group number 45. But also other chemically resistant and poorly heat-conductive materials are used.
  • the seal housing has ribs with axial channels formed therebetween.
  • the channels are preferably arranged in the outer part of the seal housing and open to the seal housing.
  • the channels can be milled into the seal housing become.
  • a cheaper way to manufacture is to make the outer part of the housing as a casting, with ribs or recesses for the channels.
  • the ribs can be attached to the seal housing individually, in groups or in the form of a ribbed body to transmit heat. This can be accomplished with shrink joints, connectors and other known techniques.
  • the channels are preferably flowed through by air. It has proved to be favorable to position on a rotating part, in particular a coupling of the pump, a fan wheel, which promotes an air flow through the channels. So that the air also flows through the inner regions of the channels, it proves useful to surround the seal housing outside with baffles.
  • the baffles can be attached to the seal housing. They surround the seal housing jacket-shaped and ensure that the air flow flows through the cross sections of the individual channels evenly.
  • Fig. 1 is a section of a multi-stage centrifugal pump shown.
  • the centrifugal pump comprises a pressure housing 1 and a stage housing 2.
  • the wheels 3 are mounted on a shaft 4 and in their entirety form the rotor.
  • the bearing of this rotor via radial bearings 5 and thrust bearing 6.
  • An axial thrust of the rotor is collected by a discharge device 7.
  • a discharge device 7 In principle, there are two different variants, such as a discharge water flowing from it can be removed according to the invention.
  • a return line 8 runs for the discharge water in the pressure housing 1.
  • the return line 8 runs in the housing cover 9 closing the pressure housing 1.
  • the housing cover 9 seals against the pressure housing 1.
  • an axial gap 11 is formed between the housing cover 9 and a shaft protection sleeve 10.
  • the axial gap 11 acts as a throttle for the pump fluid in the pump housing and prevents larger amounts of fluid flow into the space 12 of the seal housing 13 flow.
  • a mechanical seal 14 is disposed within the seal housing 13. Mechanical seals belong to the category of contact seals.
  • the mechanical seal 14 consists of two low-wear rings.
  • the sliding ring 15 rotates with the shaft 4 or with the shaft protection sleeve 10, while the counter-ring 16 bears firmly against the seal housing 13.
  • the seal housing 13 consists of the inner part 18, which surrounds the mechanical seal 14 and an outer part 19.
  • the outer part 19 is a bronze body.
  • the inner part 18 is designed as a stainless steel sleeve which has shrunk into the outer part 19. The stainless steel sleeve 18 is needed to ensure corrosion resistance, while the bronze body 19 is primarily for heat dissipation.
  • a fan wheel 21 On a coupling 20 which connects the pump to a drive, a fan wheel 21 is mounted, which blows air over the seal housing 13. The air flows through passages located between ribs of the outer part and dissipates the heat from the seal housing 13. For better air flow, the outer part 19 of the seal housing 13 is surrounded by a baffle 22.
  • Fig. 2 From the perspective view of Fig. 2 the axial channels 23 in the outer part 19 of the seal housing 13 can be seen.
  • the channels 23 are to the outer surface of the seal housing 13 open.
  • the fan 21 blows air through the channels 23.
  • baffle 27, see. Fig. 1 It is located on a shoulder 27 and improves the air flow in the channels 23. Between the baffle ends on the shoulder 27 and the housing cover 9, the channels are open and serve as an outlet for the cooling airflow.
  • the guide plate 22 ensures the forced flow of air through the inner regions of the channels 23.
  • the seal housing 13 has a projection 24 which is formed by the inner part 18 of the seal housing 13.
  • the vertical circumferential surface 25 of the projection 24 serves as a contact surface of the seal housing 13 on the housing cover 9.
  • the projection 26 of the housing cover 9 protrudes into the seal housing 13.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Sustainable Development (AREA)
  • Thermal Sciences (AREA)
  • Fluid Mechanics (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
EP10722626.8A 2009-06-04 2010-05-26 Dichtungssystem für kreiselpumpen Active EP2438305B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102009023907A DE102009023907A1 (de) 2009-06-04 2009-06-04 Dichtungssystem für Kreiselpumpen
PCT/EP2010/003210 WO2010139415A1 (de) 2009-06-04 2010-05-26 Dichtungssystem für kreiselpumpen

Publications (2)

Publication Number Publication Date
EP2438305A1 EP2438305A1 (de) 2012-04-11
EP2438305B1 true EP2438305B1 (de) 2016-01-13

Family

ID=42665226

Family Applications (1)

Application Number Title Priority Date Filing Date
EP10722626.8A Active EP2438305B1 (de) 2009-06-04 2010-05-26 Dichtungssystem für kreiselpumpen

Country Status (7)

Country Link
US (1) US8870521B2 (ru)
EP (1) EP2438305B1 (ru)
CN (1) CN102803737B (ru)
DE (1) DE102009023907A1 (ru)
ES (1) ES2567263T3 (ru)
RU (1) RU2556475C2 (ru)
WO (1) WO2010139415A1 (ru)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
RU2520777C1 (ru) * 2012-12-05 2014-06-27 Общество с ограниченной ответственностью "Балтийские магистральные нефтепроводы" (ООО "Балтнефтепровод") Способ центровки ротора насоса относительно корпуса при проведении среднего ремонта магистрального насосного агрегата
CN106468287A (zh) * 2015-08-20 2017-03-01 宇航航天装备有限公司 一种离心泵专用高速旋转接头
CA3007469C (en) 2015-12-07 2021-06-29 Fluid Handling Llc Opposed impeller wear ring undercut to offset generated axial thrust in multi-stage pump
RU2672238C1 (ru) * 2017-12-20 2018-11-12 Общество с ограниченной ответственностью "Газпром трансгаз Ухта" Способ центровки блока датчиков магнитного подвеса центробежного нагнетателя газоперекачивающего агрегата
US11218048B2 (en) 2018-12-14 2022-01-04 Nidec Motor Corporation Shaft-mounted slinger for electric motor
CN111852950A (zh) * 2020-07-21 2020-10-30 丹东克隆集团有限责任公司 高温热水泵用机械密封装置

Family Cites Families (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2221225A (en) * 1938-04-16 1940-11-12 Pacific Pump Works Balancing and leakage device for centrifugal pumps
DE903535C (de) * 1944-05-24 1954-02-08 Wesselinger Gusswerk Rheinguss Kreiselpumpe, insbesondere zur Foerderung korrodierender Fluessigkeiten
US3666375A (en) * 1969-08-26 1972-05-30 Ernest H Priest Pumping a high or low temperature fluid
US3999882A (en) * 1975-03-17 1976-12-28 Dresser Industries, Inc. Flushing and cooling system for shaft seals and pumps
DE2908733A1 (de) * 1979-03-06 1980-09-11 Gardena Kress & Kastner Gmbh Transportable motorpumpe
GB2071211A (en) * 1980-02-22 1981-09-16 Millington & Co Engs Ltd Centrifugal pumps
SU1251230A2 (ru) * 1981-10-06 1986-08-15 Ярославский Электромашиностроительный Завод Электрическа машина
JPH0247314Y2 (ru) * 1987-06-26 1990-12-12
US4884945A (en) * 1988-07-21 1989-12-05 John Crane, Inc. Dynamic seal arrangement for impeller pump
DE4230715A1 (de) 1992-09-14 1994-03-17 Klein Schanzlin & Becker Ag Entlastungswasserrückführung
US5624245A (en) * 1994-10-26 1997-04-29 Mp Pumps, Inc. Centrufugal pump with thermally isolated and dynamically air cooled shaft seal assembly
DE29503806U1 (de) * 1995-03-06 1996-07-04 Sihi GmbH & Co KG, 25524 Itzehoe Pumpe zur Förderung heißer Medien
DE19518564A1 (de) 1995-05-20 1996-11-21 Klein Schanzlin & Becker Ag Kreiselpumpe zur Förderung heißer Medien
US6287074B1 (en) * 1997-03-31 2001-09-11 Nate International Mechanical seal for shafts and axles
US20080121384A1 (en) * 2006-11-29 2008-05-29 Po-Yung Tseng Liquid cooled heat dissipator

Also Published As

Publication number Publication date
EP2438305A1 (de) 2012-04-11
ES2567263T3 (es) 2016-04-21
US8870521B2 (en) 2014-10-28
RU2011151762A (ru) 2013-07-20
WO2010139415A1 (de) 2010-12-09
CN102803737A (zh) 2012-11-28
RU2556475C2 (ru) 2015-07-10
CN102803737B (zh) 2016-03-16
US20120076643A1 (en) 2012-03-29
DE102009023907A1 (de) 2010-12-09

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