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WO2013041452A1 - Train de turbomachines - Google Patents

Train de turbomachines Download PDF

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Publication number
WO2013041452A1
WO2013041452A1 PCT/EP2012/068038 EP2012068038W WO2013041452A1 WO 2013041452 A1 WO2013041452 A1 WO 2013041452A1 EP 2012068038 W EP2012068038 W EP 2012068038W WO 2013041452 A1 WO2013041452 A1 WO 2013041452A1
Authority
WO
WIPO (PCT)
Prior art keywords
turbomachine
hydrodynamic
vibration damper
torsional vibration
strand
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.)
Ceased
Application number
PCT/EP2012/068038
Other languages
German (de)
English (en)
Inventor
Rob Eelman
Volker Hütten
Tim Christian KRAUSE
Andreas Naumann
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.)
Siemens AG
Siemens Corp
Original Assignee
Siemens AG
Siemens Corp
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 Siemens AG, Siemens Corp filed Critical Siemens AG
Publication of WO2013041452A1 publication Critical patent/WO2013041452A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D15/00—Adaptations of machines or engines for special use; Combinations of engines with devices driven thereby
    • F01D15/08—Adaptations for driving, or combinations with, 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
    • F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D17/08—Centrifugal pumps
    • F04D17/10—Centrifugal pumps for compressing or evacuating
    • F04D17/12—Multi-stage pumps
    • F04D17/122—Multi-stage pumps the individual rotor discs being, one for each stage, on a common shaft and axially spaced, e.g. conventional centrifugal multi- stage compressors
    • 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
    • F04D25/02—Units comprising pumps and their driving means
    • F04D25/06—Units comprising pumps and their driving means the pump being electrically driven
    • 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
    • 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
    • F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
    • F04D29/661—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps
    • F04D29/668—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps damping or preventing mechanical vibrations
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2260/00—Function
    • F05D2260/96—Preventing, counteracting or reducing vibration or noise

Definitions

  • the present invention relates to a
  • Turbomachinery comprising at least one
  • excitation sources of torsional vibrations are, for example, inverter-driven drive units. Due to the repeated power conversion (AC-DC-AC) can harmonic and interharmonic
  • Turbomachinery strands are initiated.
  • the interharmonic excitation frequencies are of great importance. These interharmonic excitation frequencies often have resonances with the first torsional frequency within the driving range. Due to the low damping of the turbomachine strand or the torsion system of the steel structure, resonances can lead to significantly high oscillating torsional moments. These have a negative influence on the service life of the components in the turbomachine train of a turbomachine. Furthermore, in a turbomachine train having a transmission, the torsional vibrations are coupled to the flexural vibrations. In such turbomachinery strands can
  • Torsionspendelmomente cause increased bending vibrations in the transmission.
  • a synchronous motor for example, a synchronous motor or a synchronous motor
  • Asynchronous motor at the network respectively
  • turbomachinery trains can be designed such that no torsional resonances in the operating speed range of
  • torque transmitting components are designed oversized in turbomachinery. It is also possible to block the operating speed ranges at which torsional resonances occur. Also minimizing the
  • turbomachinery strands A disadvantage of such turbomachinery strands is the inflexibility of the turbomachine strand. This means that turbomachinery trains can not run at any speed
  • Turbomachinery to be sized large. This increases the costs. Accordingly, it is the object of the present invention to provide a turbomachinery, the previously
  • the turbomachinery has at least one
  • the at least one hydrodynamic torsional vibration damper is arranged hydrodynamic torsional vibration damper.
  • vibration-technical need to be arranged at any position and number in the turbomachinery.
  • Such a trained turbomachinery allows a reduction of the torsional load, especially in the torque-transmitting strand components.
  • hydrodynamic torsional vibration damper is preferably arranged on the drive shaft of the drive unit and rotates during operation of the turbomachine strand with the Drive shaft with. Therefore, the hydrodynamic learns
  • the at least one hydrodynamic torsional vibration damper converts part of the kinetic vibration energy into heat energy.
  • the torsional stresses in the turbomachinery can be reduced. That is, by the damping property of the at least one additionally arranged hydrodynamic torsional vibration damper, the dynamic
  • Torsion load of the turbomachinery strand can be reduced.
  • Turbomachinery trains can increase the life of the components of the turbomachine train. Furthermore, by the arrangement of at least one hydrodynamic
  • the at least one, additionally provided hydrodynamic torsional vibration damper provides a possibility for natural frequency tuning of the
  • Natural frequency tuning of the turbomachine string can be done via the torsional stiffness of the hydrodynamic
  • Torsionsschwingungsdämpfers made a greater rotational speed distance to resonance states and thereby additionally occurring torsional vibrations can be reduced.
  • the at least one clutch which is designed in particular as a non-shiftable clutch, transmits
  • the purpose of the clutch is in addition to the transmission of a rotational movement or torque, the damping of torque surges.
  • Hydrodynamic torsional vibration dampers are also called hydrodynamic torsional dampers, as hydrodynamic
  • Torsional vibration damper can be on the drive shaft
  • the at least one hydrodynamic torsional vibration damper on the at least one clutch, in particular non-shiftable clutch is arranged, in particular part of at least one clutch.
  • the at least one clutch and at least one hydrodynamic torsional vibration damper can be arranged in a functional series connection.
  • the at least one hydrodynamic torsional vibration damper may comprise a flywheel ring and a hub ring. These can be part of a clutch, in particular a non-shiftable clutch.
  • the at least one hydrodynamic torsional vibration damper and the coupling are advantageously matched to one another such that torsional vibrations of the drive shaft of the
  • the at least one hydrodynamic torsional vibration damper can be a non-shiftable clutch driver disk, which is arranged as overload protection on the clutch, in particular the non-shiftable clutch, in particular on the flywheel of the clutch.
  • Turbomachinery may be provided that the at least a hydrodynamic torsional vibration damper is arranged on the at least one output shaft. If several output shafts are provided in one of
  • the turbomachine train may have more than one turbocompressor, wherein the one or more further turbocompressors is / are driven by the drive unit. That is, one or more second output shaft (s) drives the other turbo-compressor (s). In particular, between the drive shaft and the at least one other
  • Output shaft may be arranged a second clutch, preferably non-shiftable clutch, which is designed to transmit a torque from the drive shaft to the at least one further output shaft. Furthermore, between the drive unit and the at least one
  • turbomachinery strand are driven by a common drive shaft a plurality of turbocompressors.
  • a turbomachine strand is between the
  • hydrodynamic torsional vibration dampers in the range of each clutch, the torsional load in all couplings of the turbomachine strand can be reduced.
  • a first non-shiftable clutch and a first hydrodynamic torsional vibration damper, and a second non-shiftable clutch and a second hydrodynamic torsional vibration damper each increase the torsional damping in the turbomachine train and the torsional vibration system, respectively.
  • One hydrodynamic torsional vibration damper can be arranged on the one hand on the drive shaft of the drive unit and co-rotate with the drive shaft during operation of the turbomachine train. Due to the damping property of the
  • Torsional vibration damper can be the dynamic
  • Torsionsschwingungsdämpfer can be arranged on another coupling, in particular a further non-switchable coupling, or part of another coupling,
  • the hydrodynamic torsional vibration damper (s) convert a part of the torsional vibrations or the
  • Turbomachinery trains are thereby reduced.
  • To dissipate this heat energy may be advantageous that in a turbomachinery strand at least one heat removal device for removal of the at least one
  • At least one heat removal device may preferably be designed to remove the at least one heat removal device
  • Heat energy to be formed via a cooling circuit Such heat removal devices allow effective removal of the through the at least one hydrodynamic
  • Invention may be provided in a turbomachinery that in the at least one output shaft
  • turbomachine train in which the drive unit is a turboexpander, in particular a
  • Gas turbine or a steam turbine and / or a synchronous motor or an asynchronous motor.
  • synchronous motors the rotor runs exactly with the specified by the mains frequency rotating field synchronously around, while in asynchronous motors, the rotor after the rotating field in engine operation nach- and leading in generator mode.
  • a field of excitation is required for the operation of synchronous motors.
  • Asynchronous motors and synchronous motors are variable in their speed.
  • Synchronous motor infinitely variable in speed to be able to use a power electronics, such as a frequency converter, often used.
  • the at least one turbocompressor is of radial and / or axial design. So can one or more turbocompressors in turbomachinery strand as
  • Radial turbocompressor be designed as Axialturbover Noticer or as axial-radial turbocompressors.
  • turbomachinery trains are used, for example, in the oil and gas industry and in the process industry
  • turbomachinery trains are used for natural gas transport and storage or for air decomposition.
  • Turbomachinery trains can be used in addition to electric drives 5, in particular steam turbine drives or gas turbine drives.
  • FIG. 2 shows a second turbomachine train, which is designed according to the
  • FIG. 3 shows a third turbomachine train, which according to the invention design principle is formed, ig.
  • FIG. 3 shows a third turbomachine train, which according to the invention design principle is formed, ig.
  • FIG. 3 shows a third turbomachine train, which according to the invention design principle is formed, ig.
  • FIG. 3 shows a third turbomachine train, which according to the invention design principle is formed, ig.
  • FIG. 3 shows a third turbomachine train, which according to the
  • Fig. 1 shows a typical turbomachine strand 20, which is formed according to the construction principle according to the invention
  • the turbomachine 20 has a turbocompressor 1 and a drive unit 2 for driving the
  • Turbo compressor 1 on.
  • a drive shaft 3 is driven by the drive unit 2. Further, the first one
  • Turbo compressor 1 connected to an output shaft 4.
  • a clutch 5 in particular a non-shiftable clutch, is arranged.
  • the clutch 5 is for transmitting a torque from the drive shaft 3 to the Output shaft 4 is formed.
  • Between the drive unit 2 and the clutch 5 is a hydrodynamic
  • Torsional vibration damper 6 is arranged.
  • the hydrodynamic torsional vibration damper 6 may be disposed at another position in the turbomachine string 20.
  • Torsional vibration damper 6 may be arranged in the turbomachine 20 strand. Such a trained
  • Turbomachinery 20 enables a reduction of
  • the hydrodynamic torsional vibration damper 6 can for example be arranged directly on the drive shaft 3 of the drive unit 2, so that he Operation of the turbomachine strand 20 with the drive shaft 3 co-rotated.
  • Torsionsschwingungsdämpfer 6 in heat energy. Due to the arrangement of the torsional vibration damper 6 in
  • Turbomachinery 20 can torsional loads in
  • Reducing the torsional load can increase the life of the components of the turbomachine string 20.
  • Torsional vibration damper 6 between the drive unit 2 and the clutch 5, the torque transmitting components in the turbomachine 20 are made smaller, lighter and more cost effective. Likewise, the flexibility increases within the operating speed range of
  • the hydrodynamic torsional vibration damper 6 can be arranged directly on the drive shaft 3. However, the hydrodynamic torsional vibration damper 6 is preferably arranged on the coupling 5 or is part of the coupling 5, which is preferably designed as a non-switchable coupling 5. For example, the clutch 5 and the hydrodynamic torsional vibration damper 6 can be arranged in a functional series connection to one another. In particular, the hydrodynamic torsional vibration damper 6 and the coupling 5 are advantageously matched to one another such that torsional vibrations within the
  • Turbomachinery 20 can be effectively damped.
  • Torsional vibration damper 6 may be arranged at any point in the turbomachine 20 strand.
  • a hydrodynamic torsional vibration damper 6 may also be arranged on the output shaft 4.
  • Torsional vibration damper 6 may be provided.
  • FIG. 2 schematically shows a further turbomachine strand 20, which is designed according to the construction principle according to the invention.
  • an intermediate gear 11 is arranged in the turbomachine strand 20 according to FIG. 2 in the turbomachine strand 20.
  • the intermediate gear 11 is arranged between the clutch 5, which connects the drive shaft 3 to the output shaft 4, and the turbo-compressor 1.
  • a further clutch 5 is provided between the intermediate gear 11 and the turbo compressor 1.
  • the turbocompressor 1 can be operated at different rotational speeds than specified by the drive unit 2. This allows the arrangement of the intermediate gear 11 between the turbo-compressor 1 and the drive unit. 2
  • Fig. 3 shows schematically a further turbomachine strand 20, according to the construction principle of the invention is trained.
  • turbomachine strand 20 according to FIG. 2 in the case of that shown in FIG.
  • Turbomachinery 20 additionally provided a second shaft end of the drive shaft 3 of the drive unit 2. That is, starting from the drive unit 2 is a first
  • Drive unit 2 of the first turbomachine sub-string 21 is connected via a drive shaft 3, an output shaft 4 and a first, preferably non-shiftable clutch 5 and a first torsional vibration damper 6 with a
  • Turbo compressor 1 coupled. Further, between the first non-shiftable clutch 5 and the turbo compressor 1 a
  • Turbomachine sub-strings 22 are also one
  • trained turbomachinery 20 allows a
  • turbomachine strand 20 which is designed according to the construction principle according to the invention. Also in this turbomachine 20, two turbomachinery sections 21, 22 are provided. Both the first turbomachine sub-string 21, and the second
  • Turbomachinery sub-strand 22 are driven via the drive shaft 3 of the drive unit 2. At the first
  • Turbomachinery sectionstrang 21 is provided as a turbo compressor / expander 14 a Gereteturboverêtr or a Gereteturboexpander. Between this gear turbo compressor 14 and the drive unit 2, a clutch 5 and a hydrodynamic torsional vibration damper 6 is provided, which couple the drive shaft 3 with the output shaft 4. Also in the second turbomachine sub-strand 22 is the
  • Gereteturboexpander 14 is driven by an output shaft 4, wherein the output shaft 4 via a preferably non-shiftable clutch 5 and a hydrodynamic
  • Torsional vibration damper 6 is coupled to the drive shaft 3 of the drive unit 2.
  • the Gereteturbover participatr or a Gereteturboexpander 14 are a bearing block 16 and a turbine 18 connected downstream. Between the
  • At least one hydrodynamic torsional vibration damper 6 generated thermal energy can by appropriate
  • Heat removal devices which are not shown in FIGS. 1 to 4, are discharged. It can the
  • Torsionsschwingungsdämpfers 6 in a turbo compressor train 20 the torque-transmitting clutches 5 and the shaft ends can be made smaller, lighter and thus more cost-effective.
  • the arrangement of a hydrodynamic torsional vibration damper 6 within a turbo compressor train 20 the torque-transmitting clutches 5 and the shaft ends can be made smaller, lighter and thus more cost-effective.
  • Turbomachine string 20 increases flexibility during operation within the operating range of the engine
  • Turbomachinery trains 20 can also be operated at higher speeds.
  • Couplings 5 allow their own frequency
  • Attenuation of the turbomachinery strands 20 and the Torsionssystems By means of a natural frequency tuning of a turbomachine strand 20, a greater rotational speed distance to resonance states can be produced via the torsional rigidity of the hydrodynamic torsional vibration damper 6 and / or the clutches 5 used, thereby additionally reducing the occurring torsional vibrations.
  • turbomachinery trains with drives on turbo expanders, gas and / or steam turbines and asynchronous and synchronous motors and their combinations, with different types of turbocompressors radial and / or axial design, are extremely diverse. Therefore, the turbomachine strands listed here in FIGS. 1 to 4 should be regarded as typical application examples.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Abstract

La présente invention a pour objet un train de turbomachines (20), comprenant au moins un turbocompresseur (1) et une unité d'entraînement (2) pour l'entraînement du ou des turbocompresseurs (1), un arbre d'entraînement menant (3) qui est entraîné par l'unité d'entraînement (2), et au moins un arbre d'entraînement mené[AD1] (4) qui entraîne le ou les turbocompresseurs (1), caractérisé en ce qu'entre l'arbre d'entraînement (3) et le ou les arbres d'entraînement (4) est disposé un accouplement non commutable (5) qui est destiné à transmettre un couple de rotation de l'arbre d'entraînement (3) à l'arbre ou aux arbres d'entraînement (4)[AD2] , et en ce qu'entre l'unité d'entraînement (2) et le ou les turbocompresseurs (1) est disposé au moins un amortisseur des vibrations de torsion hydrodynamique (6)[AD3] . [AD1]"Antriebswelle" et "Abtriebswelle" ne peuvent en aucun cas se traduir(e de la même façon ! [AD2]en ce qu'un accouplement non commutable (5), destiné à transmettre un couple de rotation de l'arbre d'entraînement (3) à l'arbre ou aux arbres d'entraînement (4) est disposé entre l'arbre menant (3) et le ou les arbres menés (4) Ne pas hésiter à modifier l'ordre de la proposition pour alléger le style. [AD3]Même remarque que ci-dessus : en ce qu'au moins un amortisseur des vibrations de torsion hydrodynamique (6) est disposé entre l'unité d'entraînement (2) et le ou les turbocompresseurs (1)
PCT/EP2012/068038 2011-09-22 2012-09-14 Train de turbomachines Ceased WO2013041452A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102011083225A DE102011083225A1 (de) 2011-09-22 2011-09-22 Turbomaschinenstrang
DE102011083225.4 2011-09-22

Publications (1)

Publication Number Publication Date
WO2013041452A1 true WO2013041452A1 (fr) 2013-03-28

Family

ID=46875778

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2012/068038 Ceased WO2013041452A1 (fr) 2011-09-22 2012-09-14 Train de turbomachines

Country Status (2)

Country Link
DE (1) DE102011083225A1 (fr)
WO (1) WO2013041452A1 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2014180688A1 (fr) 2013-05-08 2014-11-13 Voith Patent Gmbh Transmission et installation de compresseur à transmission
EP2902737A2 (fr) 2014-01-24 2015-08-05 Air Products And Chemicals, Inc. Systèmes et procédés de compression d'air
CN109578093A (zh) * 2017-09-28 2019-04-05 福伊特专利有限公司 用于驱动做功机器的驱动设备
CN114207286A (zh) * 2019-08-07 2022-03-18 开利公司 轴流式和下游压缩机组件

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102012219854B3 (de) * 2012-10-30 2013-11-07 Siemens Aktiengesellschaft Vermeidung von Drehschwingungen bei Turbomaschinen

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FR841642A (fr) * 1938-08-02 1939-05-24 Daimler Benz Ag Commande de souffleries, en particulier pour moteurs d'avions
US2659528A (en) * 1948-09-29 1953-11-17 Lockheed Aircraft Corp Gas turbine compressor system
DE915022C (de) * 1940-06-14 1954-07-15 Gutehoffnungshuette Sterkrade Maschinensatz zur Leistungssteigerung von Kreiselverdichtern oder Kreiselpumpen durch Drehzahlerhoehung ueber einen gewaehlten Normalpunkt hinaus
US3955365A (en) * 1973-12-26 1976-05-11 The Garrett Corporation Fluid coupled drive apparatus
DE3441877A1 (de) * 1984-11-16 1986-05-22 Voith-Turbo Gmbh & Co Kg, 7180 Crailsheim Kraftuebertragungsaggregat zum antrieb einer drehzahlvariablen arbeitsmaschine
WO2002012692A1 (fr) * 2000-08-10 2002-02-14 Conocophillips Company Convertisseur de couple pour lancement de compresseur
US20090054191A1 (en) * 2006-03-06 2009-02-26 Holt Christopher G Dual End Gear Fluid Drive Starter

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DE4429855C1 (de) * 1994-08-23 1995-08-17 Daimler Benz Ag Aufgeladene Brennkraftmaschine mit mechanischer Hochtriebsmöglichkeit eines Abgasturboladers
DE19846445A1 (de) * 1998-08-27 2000-03-02 Mannesmann Sachs Ag Torsionsschwingungsdämpfer an einer Überbrückungskupplung mit Planetengetriebe
DE102006004877A1 (de) * 2006-02-03 2007-08-16 Daimlerchrysler Ag Turboverbundsystem
DE102006011987A1 (de) * 2006-03-16 2007-09-20 Daimlerchrysler Ag Antriebsstrang mit einem Turboverbundsystem
DE102008026033B4 (de) * 2008-05-30 2017-08-24 Voith Patent Gmbh Antriebsstrang mit einer hydrodynamischen Maschine
DE102009034193A1 (de) * 2009-07-22 2011-02-03 Voith Patent Gmbh Turbo-Compound-System für eine Antriebsvorrichtung

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR841642A (fr) * 1938-08-02 1939-05-24 Daimler Benz Ag Commande de souffleries, en particulier pour moteurs d'avions
DE915022C (de) * 1940-06-14 1954-07-15 Gutehoffnungshuette Sterkrade Maschinensatz zur Leistungssteigerung von Kreiselverdichtern oder Kreiselpumpen durch Drehzahlerhoehung ueber einen gewaehlten Normalpunkt hinaus
US2659528A (en) * 1948-09-29 1953-11-17 Lockheed Aircraft Corp Gas turbine compressor system
US3955365A (en) * 1973-12-26 1976-05-11 The Garrett Corporation Fluid coupled drive apparatus
DE3441877A1 (de) * 1984-11-16 1986-05-22 Voith-Turbo Gmbh & Co Kg, 7180 Crailsheim Kraftuebertragungsaggregat zum antrieb einer drehzahlvariablen arbeitsmaschine
WO2002012692A1 (fr) * 2000-08-10 2002-02-14 Conocophillips Company Convertisseur de couple pour lancement de compresseur
US20090054191A1 (en) * 2006-03-06 2009-02-26 Holt Christopher G Dual End Gear Fluid Drive Starter

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2014180688A1 (fr) 2013-05-08 2014-11-13 Voith Patent Gmbh Transmission et installation de compresseur à transmission
US10100837B2 (en) 2013-05-08 2018-10-16 Voith Patent Gmbh Transmission and geared compressor system
EP2902737A2 (fr) 2014-01-24 2015-08-05 Air Products And Chemicals, Inc. Systèmes et procédés de compression d'air
CN109578093A (zh) * 2017-09-28 2019-04-05 福伊特专利有限公司 用于驱动做功机器的驱动设备
CN109578093B (zh) * 2017-09-28 2023-12-08 福伊特专利有限公司 用于驱动做功机器的驱动设备
CN114207286A (zh) * 2019-08-07 2022-03-18 开利公司 轴流式和下游压缩机组件

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