EP0955466A1 - Etanchéité de jeu annulaire - Google Patents

Etanchéité de jeu annulaire Download PDF

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Publication number
EP0955466A1
EP0955466A1 EP98106690A EP98106690A EP0955466A1 EP 0955466 A1 EP0955466 A1 EP 0955466A1 EP 98106690 A EP98106690 A EP 98106690A EP 98106690 A EP98106690 A EP 98106690A EP 0955466 A1 EP0955466 A1 EP 0955466A1
Authority
EP
European Patent Office
Prior art keywords
pressure
machine according
sealing
stage
seal
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
EP98106690A
Other languages
German (de)
English (en)
Other versions
EP0955466B1 (fr
Inventor
Jens-Uwe Brandt
Gerhard Rohlfing
Vejen Hristov
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.)
ITT Bornemann GmbH
Original Assignee
Joh Heinr Bornemann GmbH
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 Joh Heinr Bornemann GmbH filed Critical Joh Heinr Bornemann GmbH
Priority to EP98106690A priority Critical patent/EP0955466B1/fr
Priority to ES98106690T priority patent/ES2187848T3/es
Priority to DE59806719T priority patent/DE59806719D1/de
Priority to DK98106690T priority patent/DK0955466T3/da
Priority to AT98106690T priority patent/ATE230070T1/de
Priority to RU98123617/06A priority patent/RU2218480C2/ru
Priority to JP00493399A priority patent/JP4152513B2/ja
Priority to NO19990860A priority patent/NO323251B1/no
Priority to CA002262849A priority patent/CA2262849C/fr
Priority to KR10-1999-0008053A priority patent/KR100527525B1/ko
Priority to US09/272,167 priority patent/US6129533A/en
Priority to BR9902040-8A priority patent/BR9902040A/pt
Priority to CN99105562A priority patent/CN1131377C/zh
Publication of EP0955466A1 publication Critical patent/EP0955466A1/fr
Application granted granted Critical
Publication of EP0955466B1 publication Critical patent/EP0955466B1/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
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0003—Sealing arrangements in rotary-piston machines or pumps
    • F04C15/0034—Sealing arrangements in rotary-piston machines or pumps for other than the working fluid, i.e. the sealing arrangements are not between working chambers of the machine
    • F04C15/0038—Shaft sealings specially adapted for rotary-piston machines or pumps

Definitions

  • the invention relates to a fluid-carrying machine, in particular a pump, with a component rotating in a stationary housing part within an annular gap, the stationary housing part separating an interior having a higher product pressure from an exterior having a lower pressure, in which the rotating component is mounted in an external bearing , which is sealed from the interior by a sealing system.
  • the invention relates to a screw pump with at least one feed screw, which is enclosed by a housing which has at least one suction port and at least one pressure port, the suction port being connected to a suction space upstream of the feed screw and the pressure port being connected to a pressure space downstream of the feed screw, of the devices for separating the respective liquid phase from the gas phase of the medium stream emerging from the feed screw and has a lower section for receiving at least a portion of the separated liquid phase, a liquid short-circuit line being connected to this lower pressure chamber section communicates with the suction chamber and, together with the conveying elements, forms a closed circuit for a quantity of liquid required for permanent sealing.
  • a liquid short-circuit line being connected to this lower pressure chamber section communicates with the suction chamber and, together with the conveying elements, forms a closed circuit for a quantity of liquid required for permanent sealing.
  • the invention has for its object to develop a machine of the type described above with an improved sealing system for the rotating component.
  • this object is achieved according to the invention in that the annular gap is formed between two extremely hard, wear-resistant materials slide bearing shells, which form a first pressure reduction stage according to the principle of action of a radial slide bearing, the one in the axial direction Leakage from this first sealing stage in the conveying process of the turbomachine returning device is connected downstream, which is followed by a second sealing stage in the axial direction, which is designed as a simple seal in the form of a lip seal and / or a simple mechanical seal.
  • a two-stage sealing system is thus provided.
  • the first stage is used to reduce pressure and uses the principle of action of a radial plain bearing with the construction of a hydrodynamic wedge.
  • the plain bearing shells can be made from solid industrial ceramics (e.g. based on aluminum oxide or zirconium oxide), from solid hard metals (e.g. based on silicon carbide or tungsten carbide) or from coated metals (e.g. hard chrome plating, tungsten carbide or chromium oxide coating).
  • the structure of this first sealing stage has the advantage that, on the one hand, an effective hydrodynamic lubricating wedge is built up from the liquid in the pumped medium, but, on the other hand, any particles that have penetrated into the annular gap are simply ground between them due to the extreme hardness and wear resistance of the plain bearing shells.
  • the feedback of the leakage of the first sealing stage can e.g. B. by suitable pressure drop between the outlet and inlet side of the machine (with the outlet-side arrangement of the seal) or z. B. by external tools such. B. a pump (with inlet-side arrangement of the seal).
  • the second sealing stage provided according to the invention minimizes the leakage at the lowest differential pressures in order to protect the environment or mechanical functional elements.
  • the second sealing stage can be designed as a simple sealing system in the form of a lip sealing ring or a single-acting mechanical seal.
  • the second Seal stage can also be designed as a multiple circuit of sealing systems of conventional design z. B. as a lip seal with a downstream mechanical seal or as a V-ring with a downstream lip seal and a downstream mechanical seal.
  • Figure 1 shows a previously known (see DE 43 16 735 C2) screw pump, which has two contactless intermeshing, opposing pairs of conveying screws as conveying elements, each comprising a right-handed screw 1 and a left-handed screw 2.
  • the interlocking conveyor screws together with the housing surrounding them, form 3 individually closed delivery chambers.
  • the torque is transmitted from the drive shaft to the driven shaft by means of a gear transmission 4 arranged outside the pump housing 3.
  • the pump housing 3 has a suction nozzle 5 and a pressure nozzle 6.
  • the medium 9 flowing to the pump through the suction nozzle 5 is supplied in the pump housing 3 in two partial flows to the respective central suction chamber 10, that of the associated delivery screw 1 or 2 is connected upstream. Downstream of these feed screws is a pressure chamber 11, which is closed axially outwards by a shaft seal 12, which is used to seal an outer bearing 13.
  • a liquid short-circuit line 14 is connected, which is connected to the suction chamber 10.
  • the partial liquid volume flow separated on the pressure side from the conveyed liquid-gas mixture and metered back into the suction area is identified by arrow 15 and is conveyed again as a liquid circulation from the suction chamber 10 into the pressure chamber 11.
  • the liquid level in the pump housing 3 or pressure chamber 11 can generally be below the shafts 7, 8.
  • the wetting of the shaft seals 12 as a result of the direct inflow is generally sufficient for sufficient lubrication of these shaft seals 12.
  • FIG. 1 shows an embodiment of the invention.
  • a component rotates within an annular gap 17, which is the shaft 8 of FIG. 1.
  • the stationary housing part 16 separates an interior having a higher product pressure, which is the pressure chamber 11 of FIG. 1, from an outer chamber 18 having a lower pressure, in which the shaft 8 is mounted in an outer bearing 13, which is opposite the pressure chamber 11 is sealed by the following sealing system:
  • the annular gap 17 is formed between two slide bearing shells 19 made of extremely hard, wear-resistant materials, which are elastically supported by O-rings 20 to compensate for misalignments in the radial direction.
  • the first pressure reduction stage formed by the slide bearing shells 19 is followed in the axial direction by a feedback device 21 which transfers this leakage from the first sealing stage into the conveying process of the turbomachine, for which a separate pump 23 can be provided.
  • a separate pump 23 can be provided.
  • the feedback device 21 is seen in the axial direction downstream of a second sealing stage 22, which as a simple seal z. B. can be formed in the form of a lip seal.
  • FIG. 3 shows a screw pump according to FIG. 1 with a sealing system according to the invention, shown only schematically, according to FIG. 2 and a pressure compensation device 24 according to the invention, which is additionally provided or be formed by a bladder accumulator.
  • the pressure compensation device 24 ensures that the same pressure level prevails in the installation space as in the suction space 10. This arrangement is particularly advantageous in the case of changing pressures in the suction space 10, so as to minimize the pressure differences at the second sealing stage 22.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Rotary Pumps (AREA)
  • Medicines Containing Plant Substances (AREA)
  • Adhesives Or Adhesive Processes (AREA)
  • Liquid Crystal Substances (AREA)
  • Sealing With Elastic Sealing Lips (AREA)
  • Sealing Of Bearings (AREA)
  • Mechanical Sealing (AREA)
  • Prostheses (AREA)
  • Electrical Discharge Machining, Electrochemical Machining, And Combined Machining (AREA)
EP98106690A 1998-04-11 1998-04-11 Etanchéité de jeu annulaire Expired - Lifetime EP0955466B1 (fr)

Priority Applications (13)

Application Number Priority Date Filing Date Title
EP98106690A EP0955466B1 (fr) 1998-04-11 1998-04-11 Etanchéité de jeu annulaire
ES98106690T ES2187848T3 (es) 1998-04-11 1998-04-11 Maquina que conduce fluidos.
DE59806719T DE59806719D1 (de) 1998-04-11 1998-04-11 Spaltringdichtung
DK98106690T DK0955466T3 (da) 1998-04-11 1998-04-11 Tætning til ringformet spalte
AT98106690T ATE230070T1 (de) 1998-04-11 1998-04-11 Spaltringdichtung
RU98123617/06A RU2218480C2 (ru) 1998-04-11 1998-12-28 Машина для перемещения текучих сред (варианты)
JP00493399A JP4152513B2 (ja) 1998-04-11 1999-01-12 液体送り装置
NO19990860A NO323251B1 (no) 1998-04-11 1999-02-23 Spalteringtetning
CA002262849A CA2262849C (fr) 1998-04-11 1999-02-23 Systeme d'etancheite ameliore pour l'element rotatif d'une pompe
KR10-1999-0008053A KR100527525B1 (ko) 1998-04-11 1999-03-11 환상 틈새형 밀봉 구조를 갖는 스크류 펌프
US09/272,167 US6129533A (en) 1998-04-11 1999-03-18 Sealing system for rotating component of a pump
BR9902040-8A BR9902040A (pt) 1998-04-11 1999-04-12 Máquina condutora de fluido.
CN99105562A CN1131377C (zh) 1998-04-11 1999-04-12 缝隙环密封

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP98106690A EP0955466B1 (fr) 1998-04-11 1998-04-11 Etanchéité de jeu annulaire

Publications (2)

Publication Number Publication Date
EP0955466A1 true EP0955466A1 (fr) 1999-11-10
EP0955466B1 EP0955466B1 (fr) 2002-12-18

Family

ID=8231756

Family Applications (1)

Application Number Title Priority Date Filing Date
EP98106690A Expired - Lifetime EP0955466B1 (fr) 1998-04-11 1998-04-11 Etanchéité de jeu annulaire

Country Status (13)

Country Link
US (1) US6129533A (fr)
EP (1) EP0955466B1 (fr)
JP (1) JP4152513B2 (fr)
KR (1) KR100527525B1 (fr)
CN (1) CN1131377C (fr)
AT (1) ATE230070T1 (fr)
BR (1) BR9902040A (fr)
CA (1) CA2262849C (fr)
DE (1) DE59806719D1 (fr)
DK (1) DK0955466T3 (fr)
ES (1) ES2187848T3 (fr)
NO (1) NO323251B1 (fr)
RU (1) RU2218480C2 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2008116590A1 (fr) * 2007-03-23 2008-10-02 Ghh Rand Schraubenkompressoren Gmbh Bague d'étanchéité pour des joints d'arbre
DE202017107379U1 (de) 2017-12-04 2017-12-18 SKF Lubrication System Germany GmbH Schmierfettpumpe
DE102017221847A1 (de) 2017-12-04 2019-06-06 Skf Lubrication Systems Germany Gmbh Schmierfettpumpe und Verfahren zur Verwertung von Leckagefett einer Schmierfettpumpe

Families Citing this family (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1327078B1 (fr) 2000-10-18 2009-05-06 LEYBOLD VACUUM GmbH Rotor a vis a plusieurs etages
GB2371838B (en) * 2001-02-02 2004-07-21 Federal Mogul Rpb Ltd Thrust Bearing Arrangement
US20080169157A1 (en) * 2002-12-02 2008-07-17 Wyker Christopher A Lip seal lubrication reservoir and method of level control
CN1536801B (zh) * 2003-04-07 2010-04-28 华为技术有限公司 一种网络侧以及用户侧的媒质接入控制层处理单元
ZA200507096B (en) 2004-09-07 2006-06-28 Crane John Inc Sealing system for slurry pump
WO2007000815A1 (fr) * 2005-06-29 2007-01-04 Mayekawa Mfg. Co., Ltd Procédé d’arrivée d’huile et dispositif pour compresseur à vis à deux étages, et procédé de commande d’un dispositif de réfrigération
US20080003099A1 (en) * 2006-06-30 2008-01-03 Honeywell International, Inc. Closed bias air film riding seal in event of housing breach for shared engine lubrication accessory gearboxes
US8342156B2 (en) * 2009-08-27 2013-01-01 O'shea Fergal Michael Bearing arrangement for a pump
US20120306156A1 (en) * 2011-06-01 2012-12-06 Alma Products Company Compressor seal
DE102012001700B4 (de) * 2012-01-31 2013-09-12 Jung & Co. Gerätebau GmbH Zweispindelige Schraubenspindelpumpe in einflutiger Bauweise
USD749138S1 (en) 2014-12-19 2016-02-09 Q-Pumps S.A. de C.V. Twin screw pump
CN106481558B (zh) * 2015-08-27 2018-11-16 上海伊莱茨真空技术有限公司 一种用于罗茨真空泵的三唇封油密封系统
DE102020124392A1 (de) * 2020-09-18 2022-03-24 Itt Bornemann Gmbh Abstandseinstellung für doppelschneckenpumpen

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2710581A (en) * 1951-10-26 1955-06-14 New York Air Brake Co Rotary pump
US2758548A (en) * 1950-08-24 1956-08-14 Edward A Rockwell Rotary fluid displacement device and mechanism therefor
DE2740161A1 (de) * 1976-09-04 1978-03-16 Howden Compressors Ltd Verbesserungen an und in bezug auf verdichtern
GB2138074A (en) * 1983-04-09 1984-10-17 Glyco Antriebstechnik Gmbh A hydraulic pump
DE4316735A1 (de) * 1993-05-19 1994-11-24 Bornemann J H Gmbh & Co Pumpverfahren zum Betreiben einer Multiphasen-Schraubenspindelpumpe und Pumpe

Family Cites Families (14)

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Publication number Priority date Publication date Assignee Title
US1673259A (en) * 1926-03-11 1928-06-12 Stacold Corp Pump
US2549633A (en) * 1945-12-22 1951-04-17 Metals & Controls Corp Gas burner ignition and safety control system
US3527507A (en) * 1968-02-12 1970-09-08 Garlock Inc Unitary bearing element with improved,integral scraper-sealing lip
US3575426A (en) * 1968-06-24 1971-04-20 Caterpillar Tractor Co Pressurized sealing arrangement
NL162721C (nl) * 1969-02-12 1980-06-16 Cerpelli Orazio Schroefpomp.
US3589843A (en) * 1969-02-14 1971-06-29 Warren Pumps Inc Rotary pump with intermeshing helical ribs
GB1317435A (en) * 1969-06-05 1973-05-16 Turnbull Marine Design Ship propeller shaft stern bearing arrangements
JPS5951190A (ja) * 1982-09-17 1984-03-24 Hitachi Ltd オイルフリ−スクリユ−圧縮機の油切り装置
GB2165890B (en) * 1984-10-24 1988-08-17 Stothert & Pitt Plc Improvements in pumps
GB2182393A (en) * 1985-11-04 1987-05-13 Ngk Insulators Ltd Intermeshing screw pump
JPS631772A (ja) * 1986-06-20 1988-01-06 Kobe Steel Ltd 真空ポンプとその運転方法
JP2515831B2 (ja) * 1987-12-18 1996-07-10 株式会社日立製作所 スクリユ―真空ポンプ
JPH03110138A (ja) * 1989-09-25 1991-05-10 Kobe Steel Ltd タイヤユニフォミティマシンにおけるリムチエンジャ装置
JP3344825B2 (ja) * 1994-05-24 2002-11-18 栃木富士産業株式会社 スクリュー式過給機のシール装置

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2758548A (en) * 1950-08-24 1956-08-14 Edward A Rockwell Rotary fluid displacement device and mechanism therefor
US2710581A (en) * 1951-10-26 1955-06-14 New York Air Brake Co Rotary pump
DE2740161A1 (de) * 1976-09-04 1978-03-16 Howden Compressors Ltd Verbesserungen an und in bezug auf verdichtern
GB2138074A (en) * 1983-04-09 1984-10-17 Glyco Antriebstechnik Gmbh A hydraulic pump
DE4316735A1 (de) * 1993-05-19 1994-11-24 Bornemann J H Gmbh & Co Pumpverfahren zum Betreiben einer Multiphasen-Schraubenspindelpumpe und Pumpe

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2008116590A1 (fr) * 2007-03-23 2008-10-02 Ghh Rand Schraubenkompressoren Gmbh Bague d'étanchéité pour des joints d'arbre
DE202017107379U1 (de) 2017-12-04 2017-12-18 SKF Lubrication System Germany GmbH Schmierfettpumpe
DE102017221847A1 (de) 2017-12-04 2019-06-06 Skf Lubrication Systems Germany Gmbh Schmierfettpumpe und Verfahren zur Verwertung von Leckagefett einer Schmierfettpumpe

Also Published As

Publication number Publication date
NO990860D0 (no) 1999-02-23
NO990860L (no) 1999-10-12
JP4152513B2 (ja) 2008-09-17
CN1232142A (zh) 1999-10-20
CA2262849A1 (fr) 1999-10-11
RU2218480C2 (ru) 2003-12-10
BR9902040A (pt) 2000-02-22
ES2187848T3 (es) 2003-06-16
US6129533A (en) 2000-10-10
CN1131377C (zh) 2003-12-17
DK0955466T3 (da) 2003-03-03
DE59806719D1 (de) 2003-01-30
NO323251B1 (no) 2007-02-12
CA2262849C (fr) 2004-11-30
JPH11303772A (ja) 1999-11-02
KR19990082721A (ko) 1999-11-25
ATE230070T1 (de) 2003-01-15
KR100527525B1 (ko) 2005-11-09
EP0955466B1 (fr) 2002-12-18

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