EP0440902B1 - Getriebe-Turboverdichter - Google Patents

Getriebe-Turboverdichter Download PDF

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Publication number
EP0440902B1
EP0440902B1 EP90122707A EP90122707A EP0440902B1 EP 0440902 B1 EP0440902 B1 EP 0440902B1 EP 90122707 A EP90122707 A EP 90122707A EP 90122707 A EP90122707 A EP 90122707A EP 0440902 B1 EP0440902 B1 EP 0440902B1
Authority
EP
European Patent Office
Prior art keywords
gear wheel
gear
compressor
stage
pinion shafts
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.)
Expired - Lifetime
Application number
EP90122707A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0440902A1 (de
Inventor
Heinrich Dr. Prümper
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.)
Deutsche Babcock Borsig AG
Original Assignee
Deutsche Babcock Borsig 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
Family has litigation
First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=6399531&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=EP0440902(B1) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Application filed by Deutsche Babcock Borsig AG filed Critical Deutsche Babcock Borsig AG
Publication of EP0440902A1 publication Critical patent/EP0440902A1/de
Application granted granted Critical
Publication of EP0440902B1 publication Critical patent/EP0440902B1/de
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
    • F04D25/00—Pumping installations or systems
    • F04D25/02—Units comprising pumps and their driving means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D25/00—Pumping installations or systems
    • F04D25/16—Combinations of two or more pumps ; Producing two or more separate gas flows
    • F04D25/163—Combinations of two or more pumps ; Producing two or more separate gas flows driven by a common gearing arrangement
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/19—Gearing
    • Y10T74/19023—Plural power paths to and/or from gearing
    • Y10T74/19074—Single drive plural driven
    • Y10T74/19079—Parallel
    • Y10T74/19084—Spur
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/19—Gearing
    • Y10T74/19949—Teeth
    • Y10T74/19963—Spur
    • Y10T74/19972—Spur form

Definitions

  • the invention relates to a multi-stage turbo compressor driven by a gear, a so-called gear turbo compressor with the features of the preamble of claim 1.
  • a known two-stage geared turbo compressor (FR-A-885 488), the impellers of the two compressor stages are arranged on the ends of a shaft.
  • the shaft is driven by a drive gear via an intermediate gear designed as a double gear.
  • Another known turbocompressor (Dubbel Taschenbuch für den Maschinenbau 14th edition, 1981, pages 920-921) has four compressor stages, the impellers of which are arranged in pairs on two pinion shafts and are driven by a central drive gear of a single-stage transmission.
  • the volume flow changes considerably from level to level. To maintain optimal conditions, corresponding speed increases are required after every two stages.
  • the speeds of the drive shaft and the pinion shaft of the last stage to be realized for an optimal compressor are so different that the necessary ratio of greater than 1:24 can no longer be installed in a conventional transmission.
  • Pressure ratios higher than 60 can only be achieved by adding a seventh or eighth compressor stage if the indispensable properties such as controllability and high overall efficiency are to be retained.
  • the highest levels of efficiency have so far failed due to the fact that the greatest feasible transmission ratio in the known transmissions for turbocompressors is approximately 1:20.
  • the first stages thus have the highest energy density with only moderate efficiencies due to the inevitably high Mach numbers.
  • a seven-stage turbocompressor with a volume flow of 55,000 m3 / h and a pressure ratio of P A / P E 64 e.g. B. would require a speed of 35,000 rpm in the seventh stage. Only 28,000 rpm can be achieved with conventional gearboxes for turbo compressors. Therefore the overall efficiency is not optimal. It is possible to fill the fourth pinion shaft with an eighth compressor stage. But even then the fundamental problem of speed limitation with the consequences outlined remains.
  • the invention has for its object to build a transmission turbocompressor for high pressure ratios with good efficiencies and sufficient controllability.
  • the intermediate gear designed as a double gear with different gear modules, creates a gearbox for turbo compressors which, in addition to moderate speeds for the low compressor stages, also realizes very high speeds for the higher compressor stages without the number of teeth of the central drive gear being assigned to the number of teeth assigned to the higher compressor stages Pinion depends.
  • the low speeds with high tooth forces require wide toothing and a large tooth module, the high speeds with correspondingly small tooth forces require narrower wheels with a fine tooth module.
  • the intermediate gearwheel with the different tooth modules also allows the combination of two independent gearboxes for turbocompressors in one housing and allows the installation of ratios up to 40. This makes it possible to achieve optimum efficiency even with geared turbo compressors for high pressure ratios.
  • the overall efficiency improvement is more than 5%, which means considerable savings in energy costs.
  • the drawing shows a gearbox for a multi-stage turbocompressor.
  • the transmission shown serves to drive a multi-stage turbocompressor and contains a central drive gear 2 connected to a drive shaft 1.
  • the drive gear 2 meshes with two pinions, which are each arranged on a pinion shaft 3, 4.
  • the impeller of a first stage and the impeller of a second stage of the turbocompressor are arranged on the ends of the pinion shaft 3.
  • the pinion shaft 4 carries at the ends the impeller of a third and a fourth stage, which cannot be seen in the drawing. All impellers revolve in a spiral housing.
  • the drive gear 2 is followed by an intermediate gear 5, which is designed as a double gear and consists of a first gear 51 and a second gear 52, which are connected to one another and arranged on a common shaft.
  • the first gear 51 meshes with the drive gear 2, while the second gear 52 engages with pinions of further pinion shafts 6, 7, 8.
  • the pinion shafts 6, 7, 8 each have an impeller on both shaft ends, which rotates in a spiral housing.
  • the pinion shaft 6 is assigned the fifth and sixth compressor stages, the pinion shaft 7 the seventh and eighth compressor stages and the pinion shaft 8 the ninth and tenth compressor stages.
  • the second gear 52 of the intermediate gear 5 has a larger diameter than the first gear 51, which is in engagement with the drive gear 2, so that the pressure combs of the pinion shafts 6, 7, 8 can overlap via the second gear 52. Furthermore, the first gear 51 has a smaller number of teeth and a larger tooth module in comparison to the second gear 52.
  • the interposition of the intermediate gearwheel 5 described makes it possible, owing to the diversity of the tooth modules, to make the first four stages completely independent of the subsequent stages in terms of transmission technology.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Supercharger (AREA)
EP90122707A 1990-02-06 1990-11-28 Getriebe-Turboverdichter Expired - Lifetime EP0440902B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4003482A DE4003482A1 (de) 1990-02-06 1990-02-06 Getriebe-turboverdichter
DE4003482 1990-02-06

Publications (2)

Publication Number Publication Date
EP0440902A1 EP0440902A1 (de) 1991-08-14
EP0440902B1 true EP0440902B1 (de) 1994-06-22

Family

ID=6399531

Family Applications (1)

Application Number Title Priority Date Filing Date
EP90122707A Expired - Lifetime EP0440902B1 (de) 1990-02-06 1990-11-28 Getriebe-Turboverdichter

Country Status (7)

Country Link
US (1) US5154571A (ja)
EP (1) EP0440902B1 (ja)
JP (1) JP2835324B2 (ja)
CZ (1) CZ279686B6 (ja)
DE (2) DE4003482A1 (ja)
RU (1) RU2002119C1 (ja)
SK (1) SK278378B6 (ja)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5382132A (en) * 1992-12-07 1995-01-17 Bhs-Voith Getriebetechnik Gmbh Toothed wheel gear unit for a compressor system
GB2321502A (en) * 1997-01-24 1998-07-29 Europ Gas Turbines Ltd Turbocharger arrangement
EP0945400A2 (de) * 1998-03-26 1999-09-29 Krupp Uhde GmbH Verfahren zur Herstellung von Salpetersäure
DE19938492A1 (de) * 1999-08-13 2001-02-15 Man Turbomasch Ag Ghh Borsig Getriebeanordnung für einen mehrstufigen Turboverdichter
EP1691081A2 (de) 2005-01-19 2006-08-16 Man Turbo Ag Mehrstufiger Turbokompressor
EP2740941A1 (en) 2011-08-05 2014-06-11 Mitsubishi Heavy Industries Compressor Corporation Centrifugal compressor

Families Citing this family (27)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4204338C2 (de) * 1992-02-11 1993-11-18 Mannesmann Ag Getriebe-Turboverdichter
DE4234739C1 (de) * 1992-10-15 1993-11-25 Gutehoffnungshuette Man Getriebe-Mehrwellenturbokompressor mit Rückführstufen
DE4339060A1 (de) * 1993-11-16 1995-05-18 Borsig Babcock Ag Getriebeverdichter für die Verdichtung von Sauerstoff
DE4436710C2 (de) * 1994-10-14 1997-04-03 Gutehoffnungshuette Man Getriebe-Mehrwellenturbomaschine
JPH09119378A (ja) * 1995-10-25 1997-05-06 Ishikawajima Harima Heavy Ind Co Ltd ターボ圧縮機
US5775412A (en) * 1996-01-11 1998-07-07 Gidding Engineering, Inc. High pressure dense heat transfer area heat exchanger
DE19626876A1 (de) * 1996-07-04 1998-01-08 Knippenberg Werner Vorrichtung zum Entladen von pulvrigen und körnigen Gütern aus Silobehältern mittels eines Turboverdichters
DE59909914D1 (de) * 1999-07-05 2004-08-12 Getriebe Gmbh Bhs Getriebe-Turboverdichter
US6393865B1 (en) * 2000-09-27 2002-05-28 Air Products And Chemicals, Inc. Combined service main air/product compressor
US20030123972A1 (en) * 2001-10-09 2003-07-03 Quetel Ralph L. Method of standardizing compressor design
DE102008031116B4 (de) * 2008-05-29 2022-02-03 Man Energy Solutions Se Getriebeturbomaschine für einen Maschinenstrang, Maschinenstrang mit und Getriebe für Getriebeturbomaschine
IT1398142B1 (it) * 2010-02-17 2013-02-14 Nuovo Pignone Spa Sistema singolo con compressore e pompa integrati e metodo.
DE102011003525A1 (de) * 2011-02-02 2012-08-02 Siemens Aktiengesellschaft Gestufte Teilfuge an einem Getriebegehäuse
DE102012217441A1 (de) * 2012-09-26 2014-03-27 Siemens Aktiengesellschaft Getriebeverdichter
DE102012022131A1 (de) * 2012-11-13 2014-05-15 Man Diesel & Turbo Se Getriebeturbomaschine
DE102013208564A1 (de) 2013-05-08 2014-11-13 Voith Patent Gmbh Getriebe und Getriebeverdichteranlage
WO2015111169A1 (ja) * 2014-01-23 2015-07-30 三菱重工コンプレッサ株式会社 遠心圧縮機
WO2016042639A1 (ja) * 2014-09-18 2016-03-24 三菱重工コンプレッサ株式会社 圧縮機システム
DE102014221339A1 (de) * 2014-10-21 2016-04-21 Siemens Aktiengesellschaft Gestufte Teilfuge an einem Getriebegehäuse
RU2676173C2 (ru) * 2014-11-21 2018-12-26 Фойт Патент Гмбх Редуктор, редукторная турбомашина и способ монтажа редукторной турбомашины
DE102015203287A1 (de) * 2015-02-24 2016-08-25 Siemens Aktiengesellschaft Getriebeverdichtergehäuse, Getriebeverdichter
JP6049807B2 (ja) * 2015-06-08 2016-12-21 三菱重工コンプレッサ株式会社 遠心圧縮機
JP6395683B2 (ja) * 2015-09-02 2018-09-26 株式会社神戸製鋼所 圧縮機
CN207245975U (zh) * 2016-04-11 2018-04-17 阿特拉斯科普柯康珀泰克有限责任公司 具有离心式和容积式压缩级组合的集成式齿轮传动压缩机
CN107906026A (zh) * 2017-11-27 2018-04-13 江苏金通灵流体机械科技股份有限公司 汽轮机直驱齿轮增速式离心压缩机
JP2021156281A (ja) * 2021-02-01 2021-10-07 三菱重工コンプレッサ株式会社 ギアド圧縮機、ギアド圧縮機の設計方法
JP2021156290A (ja) * 2021-03-26 2021-10-07 三菱重工コンプレッサ株式会社 圧縮機システム

Family Cites Families (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE685397C (de) * 1938-04-22 1939-12-16 Siemens & Halske Akt Ges Einrichtung zum Umschalten der Ablaufgeschwindigkeit von Laufraedern in Laufwerken
US2313205A (en) * 1938-06-10 1943-03-09 Potez Henry Charles Alexandre Two-speed driving mechanism for centrifugal compressors
FR885488A (fr) * 1942-08-26 1943-09-16 Cie Des Procedes Gohin Poulenc Compresseur double pour moteur à gazogène
DE974418C (de) * 1948-10-02 1960-12-15 Demag Ag Kreiselverdichter mit mindestens vier hintereinander-geschalteten Stufen
US3001692A (en) * 1949-07-26 1961-09-26 Schierl Otto Multistage compressors
US2955924A (en) * 1955-05-23 1960-10-11 Phillips Petroleum Co Apparatus for carrying out high speed stirred reactions
US2973894A (en) * 1957-06-17 1961-03-07 Turbo Res Corp Centrifugal compressor for starting jet engines
US3060755A (en) * 1958-07-08 1962-10-30 Itt Scanning apparatus
DE2115331C3 (de) * 1971-03-30 1974-10-31 Demag Ag, 4100 Duisburg Mehrstufiger radialer Turbokompressor
US3741676A (en) * 1971-10-12 1973-06-26 Barodyne Inc Surge control for fluid compressors
US3826587A (en) * 1973-04-10 1974-07-30 Ingersoll Rand Co Centrifugal gas compressor unit
FR2231253A5 (ja) * 1973-05-21 1974-12-20 Barodyne Inc
GB1492271A (en) * 1974-01-31 1977-11-16 Poole E Centrifugal compressors
PL201127A1 (pl) * 1977-09-29 1979-09-24 Obrabiarek Precyzyj Ponar Kolo zebate o zebach srubowych
DE3707992A1 (de) * 1987-03-12 1988-09-29 Renk Tacke Gmbh Getriebe, insbesondere fuer turbinen-kompressoren

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5382132A (en) * 1992-12-07 1995-01-17 Bhs-Voith Getriebetechnik Gmbh Toothed wheel gear unit for a compressor system
GB2321502A (en) * 1997-01-24 1998-07-29 Europ Gas Turbines Ltd Turbocharger arrangement
EP0945400A2 (de) * 1998-03-26 1999-09-29 Krupp Uhde GmbH Verfahren zur Herstellung von Salpetersäure
EP0945400A3 (de) * 1998-03-26 2000-05-17 Krupp Uhde GmbH Verfahren zur Herstellung von Salpetersäure
DE19938492A1 (de) * 1999-08-13 2001-02-15 Man Turbomasch Ag Ghh Borsig Getriebeanordnung für einen mehrstufigen Turboverdichter
WO2001012994A1 (de) 1999-08-13 2001-02-22 Man Turbomaschinen Ag Ghh Borsig Getriebeanordnung für einen mehrstufigen turboverdichter
EP1691081A2 (de) 2005-01-19 2006-08-16 Man Turbo Ag Mehrstufiger Turbokompressor
EP2740941A1 (en) 2011-08-05 2014-06-11 Mitsubishi Heavy Industries Compressor Corporation Centrifugal compressor

Also Published As

Publication number Publication date
JP2835324B2 (ja) 1998-12-14
DE59006232D1 (de) 1994-07-28
RU2002119C1 (ru) 1993-10-30
DE4003482C2 (ja) 1991-11-07
US5154571A (en) 1992-10-13
CZ279686B6 (cs) 1995-06-14
DE4003482A1 (de) 1991-08-08
CS9100236A2 (en) 1991-09-15
SK278378B6 (en) 1997-02-05
JPH0518394A (ja) 1993-01-26
EP0440902A1 (de) 1991-08-14

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