EP3106670A1 - Turbocompresseur de transmission - Google Patents

Turbocompresseur de transmission Download PDF

Info

Publication number
EP3106670A1
EP3106670A1 EP15172129.7A EP15172129A EP3106670A1 EP 3106670 A1 EP3106670 A1 EP 3106670A1 EP 15172129 A EP15172129 A EP 15172129A EP 3106670 A1 EP3106670 A1 EP 3106670A1
Authority
EP
European Patent Office
Prior art keywords
compressor
shaft
gear
drive shaft
igc
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.)
Withdrawn
Application number
EP15172129.7A
Other languages
German (de)
English (en)
Inventor
Jan Weule
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
Original Assignee
Siemens 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 Siemens AG filed Critical Siemens AG
Priority to EP15172129.7A priority Critical patent/EP3106670A1/fr
Publication of EP3106670A1 publication Critical patent/EP3106670A1/fr
Withdrawn legal-status Critical Current

Links

Images

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
    • F04D25/16—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

Definitions

  • the invention relates to a transmission turbo compressor comprising a drive shaft, a first compressor shaft of a first compressor, a transmission housing, a first compressor impeller, a first compressor housing, a first drive gear, a first compressor gear, wherein the drive shaft extends along a drive shaft axis, wherein the first compressor shaft along a compressor shaft axis, wherein the first compressor impeller is attached to the first compressor shaft coaxial with the first compressor shaft axis, the first compressor gear is disposed on the first compressor shaft coaxial with the first compressor shaft axis, wherein the first drive gear is arranged on the drive shaft coaxial with the drive shaft axis, said first drive gear and the first compressor gear in the transmission housing are engaged with each other.
  • a Getriebeturbover participatr (English: integrally geared (ompressor) of the type defined is already out of the WO 2011/141439 A1 known.
  • the conventional design usually one to four compressor shafts - often called pinion shafts - to a drive shaft - which is also often called wheel shaft - arranged.
  • drive shaft axis and compressor shaft axes are aligned parallel to each other.
  • the teeth of the compressor gears and the drive gear - which usually has a significantly larger diameter than the compressor gears as a so-called large gear - mesh in the lateral surface area of the compressor shafts. In this way, the compressor shafts rotate much faster than the drive shaft.
  • the invention has taken on the task of flexibilizing the arrangement of compressors on a gear housing of a transmission compressor defined above, preferably without increasing the complexity of the transmission by additional components.
  • the drive shaft axis and the first compressor shaft axis are arranged obliquely or perpendicular to each other, does not mean that the two axes must intersect in space. According to the invention, it is more a departure from the previous design, the drive shaft axis and the compressor shaft axis always parallel to each other to order. Particularly preferred is an arrangement of the drive shaft axis and the Compressor shaft axes such that the respective direction vectors of these axes are aligned perpendicular to each other.
  • the vertical orientation is to be understood in this case as meaning that a substantially perpendicular alignment of the axes is provided in each case (haracterizing direction vectors which, at least in the context of technical inaccuracies, deviate from the strictly mathematical vertical alignment.
  • the inventively oblique or vertical arrangement of the shaft axes of drive shaft and compressor shaft which can also be referred to as a crossed arrangement or named, there are advantages, additional possibilities and simplifications. Due to the crossed arrangement of the shafts, the gear ratios of the gears are decoupled from the center distances of the compressor shafts and the drive shaft. If space between the compressor housings, which are usually designed as a spiral housing, needed, the drive shaft can be easily extended. In this case, the transmission housing is to be extended accordingly. In the case of particularly large compressor housing, this possibility is particularly interesting, so that not as in the previous solution spectrum partial intermediate waves must be used for space gain.
  • this can be stored in an advantageous development additionally radially, preferably approximately centrally between two other radial bearings.
  • the possible installation location in addition to the available installation space, is predetermined by the direction of rotation of the existing cast model of the compressor housing or volute casing.
  • the direction of rotation can be reversed by selecting the arrangement of the compressor toothed wheels to the drive toothed wheels.
  • the toothed cones of the mating of the drive gear and the compressor gear are arranged to each other, results in a different direction of rotation of the compressor shaft without other speed influencing. This possibility is particularly advantageous for large machines or double-flow arrangements, so that the use of the existing casting models is in any case possible.
  • Radial or centrifugal compressors are usually preferred as compressors for mounting on the transmission housing.
  • an expander instead of a compressor, an expander can also be connected to the transmission housing or a corresponding compressor shaft.
  • the advantages of the Gereteturboverêtêt whors invention come in particular in a variant to bear, in addition to the at least first compressor shaft and at least a second compressor shaft of a second compressor with a compressor impeller and a second compressor housing and a corresponding second compressor gear is provided, the second compressor shaft axis as well as the first compressor shaft axis is preferably arranged perpendicular or obliquely to the drive shaft axis.
  • a plurality of additional compressors can be provided as part of the transmission turbo compressor in the same way. In this description For example, these compressors and associated components are simply numbered and the numerals are used with a continuous index.
  • the compressor shafts For the purpose of the oblique or vertical arrangement of the compressor shafts to the drive shaft, it invention preferably provides the execution of the pairings of the compressor gears with the drive gears as bevel gear.
  • the trained as bevel gears drive gears and compressor gears are formed in this case in an advantageous development than straight-toothed, helical or arc-toothed bevel gears.
  • Particularly preferred is the formation of the bevel gears of the bevel gear as Hypoidkegelzier, so that the compressor shaft axes can have a spatial distance to the drive shaft axis.
  • This spatial distance is particularly preferably designed such that both the drive shaft and the compressor shaft can continue along the respective axes preferably unattenuated in both axial directions of the corresponding bevel gear starting and accordingly the compressor shaft at both shaft ends can drive a compressor provided there or the drive shaft has further drive gears of further bevel gear drives for driving further compressor shafts.
  • the inventive design of a Getriebeturbover confusers has the further advantage that a particularly large designed compressor gear that is designed as bevel gear, in particular, if it is designed as Hypoidkegelrad allows a relatively low compressor shaft speed during operation, as in particular for a large compressor rotor of rotor dynamic Reasons is required.
  • the compressor gear simultaneously results in a particularly high installation location in a preferably horizontally oriented drive shaft when the compressor shaft axis is provided above the drive shaft axis, so that at the same time vertical space requirement of the compressor housing is taken into account.
  • Another advantageous embodiment of the invention provides that are formed on the backs of splines of the compressor gears thrust bearings that absorb an axial thrust or residual thrust from the compressor in the axial direction or compensate.
  • the orientations of the compressor and the installation locations can be chosen so that the axial forces from the impeller on the compressor shaft and the toothing forces to a large extent, especially in interpretive operating points, compensate.
  • the arrangement of at least one thrust bearing directly on the toothed cone of a compressor gear is particularly favorable for the voltage curve in the compressor shaft. As a result, if necessary, deflections of the shaft can be reduced.
  • the degrees of freedom according to the invention in the arrangement of the compressor housing provide installation locations for the compressor shaft or compressor and compressor housing, which allow the best possible balance of impeller forces and Vernierungs adoptedn, in particular such that the compressor shaft operates as axially as possible without shearing and the load on the thrust bearing is minimized.
  • An advantageous development for better distribution of bearing forces in radial bearings of the compressor shafts provides that an axial distance of a first radial bearing for a compressor shaft in the direction of each of a middle force transmission plane radial toothing forces of the corresponding compressor gear on the side of the toothing the bevel gear of the bevel gear is at least as large as the axial distance of this force introduction plane to a second radial bearing of this compressor shaft on the side facing away from the toothing side.
  • a compressor or drive shaft compressor which is arranged directly on the drive shaft, is arranged on the transmission housing on the front side.
  • the drive shaft drives a compressor on both end faces of the gear housing or the corresponding rotors of these drive shaft compressors are part of the drive shaft.
  • the drive shaft has an axial compressor as a component and, in a particularly advantageous development of this axial compressor, carries out a pre-compression before entry into the compressor of the compressor shafts.
  • the integration of compressors in the drive shaft does not mean that the drive shaft is formed integrally with the rotor of the drive shaft compressor.
  • couplings are used between the compressor rotor and the adjacent rotating components.
  • the drive shaft is partially designed as a compressor rotor, that the intermeshing between the drive shaft and the compressor gears are aligned such that there is a maximum thrust compensation in the axial direction for the drive shaft, so that a thrust bearing of the drive shaft only a relatively small Has to compensate for thrust.
  • the gear turbo compressor an almost arbitrary number of stages of the gear turbo compressor can be achieved, wherein the number of compressor shafts which can be connected to a drive shaft is of course limited by the power that can be transmitted by means of the compressor shaft.
  • compressor shafts or the drive shaft itself it is also possible for compressor shafts or the drive shaft itself to drive compressor shafts aligned parallel to the respective shafts by means of additional helical gears, and in this way to realize the use of additional compressor stages or compressors. Accordingly, it is basically possible in an advantageous development of the invention that some compressor shafts are driven by the drive shaft by means of bevel gearboxes, in particular hypoid gears and accordingly obliquely, in particular vertically (the invention uses the attribute "oblique” in principle synonymous with "not parallel”) in their Achsausides the drive shaft axis are arranged and other compressor shafts either parallel to the drive shaft aligned by a spur gear directly driven by the drive shaft or driven by already obliquely or perpendicular to the drive shaft aligned compressor shafts by means of a spur gear.
  • the operational layout of the transmission turbo compressor according to the invention is such that the drive shaft is aligned horizontally.
  • compressor shafts it is also possible and preferred within the scope of the invention for compressor shafts to be positioned in their axis extension above or below the drive shaft axis.
  • This possibility is implemented in a particularly advantageous manner with a mechanical coupling of the drive shaft and the compressor shaft by means of a hypoid gear.
  • a special advantageous development in this context provides that this so spaced from the drive shaft compressor shaft at both shaft ends drives a compressor which is mounted on the transmission housing in the manner of a Getriebeturboverêtrs.
  • the gear turbo compressor according to the invention advantageously allows arrangements in which a drive directly - without intermediate gear - drives the Getriebeturboverêtr invention.
  • Such drives are, for example, high-speed turbomachinery or electric motors.
  • the space required by the compressors on the gearbox is typically made by means of a large gear having such a large diameter that the individual compressor casings can be mounted side by side on one or two opposite sides of the gearbox.
  • the large gear driving the individual pinions or small gears of the compressor shafts causes a regularly high transmission ratio of the drive shaft to the compressor shafts.
  • the drive shaft must have a much lower rotational speed than the compressor shafts and must also be able to transmit a high torque - that is to say be designed to be quasi-statically resilient as well.
  • high-speed drives for example gas turbines, steam turbines or high-speed electric motors.
  • the required relatively low input speed in the Gereteturbover confuser conventional design therefore requires an intermediate gear. Since the invention decouples the gear ratio of the transmission of the gear compressor from the space available for the compressor, the transmission ratio between the drive shaft and the individual compressors of the Gereteturboverêt confusers can be chosen freely. Demenschend you can always interpret the Gereteturbover Noner such that no intermediate gear is necessary.
  • An added benefit of Invention may result from the fact that the drive shaft can be guided from the front side of the transmission housing and the compressors are at least partially arranged, for example, rotated by 90 ° to the drive train.
  • a preferred development of the invention provides that form due to the offset between the drive shaft and some compressor shafts, the transmission housing with at least two parting joints or parting plane with horizontal extent.
  • the first part of the joint plane between a lower part and a central part can be arranged in this way the drive shaft or lying below the drive shaft compressor shafts.
  • the drive shaft In the overlying part of the joint plane between a central part or first Mitteilteil and an upper part or second middle part, the drive shaft may be provided. Should there be more compressor shafts over the drive shaft, a further parting plane is provided between the second middle part and an upper part. Alternatively, a top part follows directly onto the lower middle section.
  • the number of partial joints preferably corresponds to the number of planes that are horizontally clamped by the various shaft axes of the transmission turbo-compressor.
  • the number of planes can be reduced particularly preferably by combining shaft axes, which can be combined to form a group within the framework of the diameters of their shafts, in a common partial joint plane. In this way, it is possible to provide guided out of the gear housing shaft ends with bearings and seals, particularly easy in the parting line accessible so to assemble and maintain.
  • partial joints may also be provided with a step for the purpose of reducing the parting plane, so that compressor shafts or drive shafts in a common parting joint can be combined for the above purpose, even if the shaft axes have a greater vertical distance from one another.
  • An advantageous development of this variant provides that the steps in the parting lines can be sealed by means of externally mounted sealing strips, wherein the sealing strips can be particularly preferably designed as a carrier of seals. Such a construction already shows the protective right DE 10 2014 219 217.8 ,
  • FIG. 1 schematically represented inventive arrangement A comprising a Getriebeturbover Noticer IGC according to the invention additionally has a drive DR and a drive shaft compressor DSC, wherein the drive DR via a first clutch (L1 with the drive shaft compressor DSC is in torque transmitting connection and the drive shaft compressor DSC via a second clutch (L2
  • the drive shaft DS with the drive shaft compressor DSC extends along a drive shaft axis DSX
  • the gear turbo compressor IGC receives the drive power for compressors (i, (1, (2, () by means of the drive shaft DS. 3, (4.
  • the first compressor (1) has a first compressor housing (C1 and a first compressor housing (C1) arranged in the first compressor housing (C1) for the other identically constructed compressor housing (Ci, (C1 to (C4, compressor impellers (Ii, (I1 to (I4 and compressors (i, (1 to (4) of the first compressor shaft (S1, the first compressor (1 and the third Compressors (3 driven.) From the second compressor shaft (S2 are driven the second compressor (2 and the fourth compressor (4).)
  • the compressor housing (C1 to (C4 are outside the gearbox GC arranged and preferably mounted there at the points where each Shaft end of a compressor shaft (S1, (S2 protrudes from the gearbox GC.) In the gearbox GC bevel gear BG1, BG2 - as in FIG.
  • the transmission housing GC has a first gearbox housing GC1, a second gearbox housing GC2 and a third gearbox housing GC3, wherein the first gearbox housing is a lower part, the second gearbox housing a middle part and the third gearbox housing a top part.
  • the first gearbox housing GC1 is designed to be separable from the second gearbox housing by means of a first parting line SPP1, and a second parting line SPP2 releasably secures the second gearbox housing GC2 from the third gearbox housing GC3.
  • the drive shaft DS is aligned horizontally, as well as the parting joints SPP1, SPP2.
  • the parting lines SPP1, SPP2 are respectively provided in the regions of passages of the drive shaft DS or the compressor shafts DS1, DS2 through the walls of the transmission housing GC, so that a simple assembly of the individual shafts can take place in each case lifted subcases GC1, GC2.
  • a spur gear FGC transmits the torque from the first compressor shaft (S1 to the third compressor shaft (S3. that in addition to the invention oblique, in particular aligned perpendicular to the drive shaft compressor shafts aligned parallel to the drive shaft or to other compressor shafts and from the parallel waves - preferably by means of spur gear driven compressor waves.
  • the FIG. 2 shows as an alternative to extending over the entire housing continuous planar parting line extending over a whole horizontal cross-section of the gear housing GC, the possibility to provide different parting planes in a single stepped parting or housing division.
  • the transmission housing GC comprises a first sub-housing GC1 and a second sub-housing GC2, wherein three different sub-joint planes SPP1, SPP2, SPP3 are implemented by means of stages STP1, STP2, STP3 in the parting line.
  • the drive shaft DS extends in the first partial plane SPP1 and the first compressor shaft axis SCX1 for the first compressor shaft (S1 is in the area of the third partial plane SPP3.)
  • a second second parting plane SPP2 allows easy mounting of the second compressor shaft (S2, which extends) extends along the second compressor shaft axis SCX2.
  • FIG. 1 Schematically exemplarily shows that at least the vertically extending part of the joint sections, so the steps STPi by means of sealing strips SB, which may be formed as a seal carrier (see also German patent application with the filing sign: DE102014221339 ), so that any leakage of the oil in the transmission housing GC is sufficiently reliably excluded.
  • FIG. 3 shows by way of example in detail how torque is transmitted from the drive shaft DS to the compressor shafts (S1, S2) by means of bevel gearboxes BG1, BG2
  • the first bevel gearbox BG1 comprises a first compressor gearwheel (G1 and a first drive gearwheel DG1
  • the respective gears are formed as Hypoidkegeliza, so that the compressor shaft axes (SX1, (SX2 of the drive shaft axis DSX have a sufficient distance, so that the two waves can be passed undisturbed past each other
  • S1, (S2, (Si) both shaft ends protrude from the gearbox GC for mounting compressors (1, ..., (n.
  • the drive shaft DS Due to its length, the drive shaft DS is supported by means of three radial bearings RBD1, RBD2, RBD3. If the axial guidance by the two bevel gear BG1, BG2 not be sufficient to determine the axial position of the drive shaft DS or compensate for thrusts in the axial direction, can be provided in a manner not shown, an additional thrust bearing for unilateral or bilateral Axialschub technique.
  • the toothed cones PC of the compressor toothed wheels (G1, (G2 are preferably arranged axially oriented in such a way that the axial thrust is compensated as far as possible from the respective impeller (I1, (I2, (Ii, 7) Since the axial thrust compensation can not be ensured in every operating situation can, is Preferably, the toothed cone PC executed at least on the back facing away from the toothing back as thrust bearing AX, which always has a thrust balance in the axial direction and a defined axial position for the compressor shaft (S1, (Si or for the entire compressor (1, (i, ... is guaranteed.
  • the radial bearing of the compressor shafts (SI by means of radial bearings RBC1, RBC2 is preferably such that a distance of a first radial bearing RBC1 in the direction of the respective compressor shaft axis (SXi from a central force introduction plane PP1 radial Veryakungs adopted of the corresponding compressor gear (Gi on the side of the teeth of the bevel gear of the bevel gear BGi is at least as large as the axial distance of the force introduction plane PP1 to the second radial bearing RBC2 on the side facing away from the toothing side.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
EP15172129.7A 2015-06-15 2015-06-15 Turbocompresseur de transmission Withdrawn EP3106670A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP15172129.7A EP3106670A1 (fr) 2015-06-15 2015-06-15 Turbocompresseur de transmission

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP15172129.7A EP3106670A1 (fr) 2015-06-15 2015-06-15 Turbocompresseur de transmission

Publications (1)

Publication Number Publication Date
EP3106670A1 true EP3106670A1 (fr) 2016-12-21

Family

ID=53476688

Family Applications (1)

Application Number Title Priority Date Filing Date
EP15172129.7A Withdrawn EP3106670A1 (fr) 2015-06-15 2015-06-15 Turbocompresseur de transmission

Country Status (1)

Country Link
EP (1) EP3106670A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3581802A1 (fr) 2018-06-14 2019-12-18 Siemens Aktiengesellschaft Dispositif et procédé d'appui d'un rotor de turbomachine radiale
EP3594506A1 (fr) 2018-07-12 2020-01-15 Siemens Aktiengesellschaft Bague de contour pour un compresseur
DE102020200235A1 (de) 2020-01-10 2021-07-15 Thyssenkrupp Ag Verfahren und Anlage zur Herstellung von Salpetersäure

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB456963A (en) * 1935-05-23 1936-11-18 Walther Voith Driving mechanism for control pumps for filling the circuits of hydraulic power transmitters
US2335445A (en) * 1943-01-11 1943-11-30 Richard Edgar Fluid discharging apparatus
DE1908005A1 (de) * 1969-02-18 1970-09-03 Demag Ag Mehrstufen-Kegelradgetriebe-Verdichter
WO2011141439A1 (fr) 2010-05-11 2011-11-17 Siemens Aktiengesellschaft Compresseur à engrenage multiétagé
WO2014195632A1 (fr) * 2013-06-06 2014-12-11 Snecma Boîtier d'entraînement des accessoires pour un turbopropulseur

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB456963A (en) * 1935-05-23 1936-11-18 Walther Voith Driving mechanism for control pumps for filling the circuits of hydraulic power transmitters
US2335445A (en) * 1943-01-11 1943-11-30 Richard Edgar Fluid discharging apparatus
DE1908005A1 (de) * 1969-02-18 1970-09-03 Demag Ag Mehrstufen-Kegelradgetriebe-Verdichter
WO2011141439A1 (fr) 2010-05-11 2011-11-17 Siemens Aktiengesellschaft Compresseur à engrenage multiétagé
WO2014195632A1 (fr) * 2013-06-06 2014-12-11 Snecma Boîtier d'entraînement des accessoires pour un turbopropulseur

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3581802A1 (fr) 2018-06-14 2019-12-18 Siemens Aktiengesellschaft Dispositif et procédé d'appui d'un rotor de turbomachine radiale
WO2019238366A1 (fr) 2018-06-14 2019-12-19 Siemens Aktiengesellschaft Dispositif, procédé
EP3594506A1 (fr) 2018-07-12 2020-01-15 Siemens Aktiengesellschaft Bague de contour pour un compresseur
WO2020011471A1 (fr) 2018-07-12 2020-01-16 Siemens Aktiengesellschaft Turbomachine radiale et procédé pour son fonctionnement
DE102020200235A1 (de) 2020-01-10 2021-07-15 Thyssenkrupp Ag Verfahren und Anlage zur Herstellung von Salpetersäure
WO2021140023A1 (fr) 2020-01-10 2021-07-15 Thyssenkrupp Industrial Solutions Ag Procédé et installation de production d'acide nitrique

Similar Documents

Publication Publication Date Title
DE102008031116A1 (de) Getriebeturbomaschine für einen Maschinenstrang, Maschinenstrang mit und Getriebe für Getriebeturbomaschine
DE102014225136A1 (de) Getriebeverdichter, Anordnung mit einem Antrieb und einem Getriebeverdichter
DE102009042504A1 (de) Stützstruktur einer Welle, und Untersetzungsgetriebe
EP3026262B1 (fr) Éolienne doté d'une chaîne cinématique
EP3045686A1 (fr) Agencement pour fixer une volute sur un boîtier de transmission et compresseur à engrenages avec un tel agencement
DE102011112255A1 (de) Hilfsgerätegetriebeeinrichtung für ein Triebwerk
WO2018153403A1 (fr) Dispositif de propulsion pour un véhicule automobile
EP3106670A1 (fr) Turbocompresseur de transmission
DE102010014588A1 (de) Kraftwerksstrang mit einer drehzahlvariablen Pumpe
EP2994646B1 (fr) Transmission et installation de compresseur à transmission
WO2014195390A1 (fr) Compresseur à engrenage
EP3221590B1 (fr) Réducteur et turbomachine à réducteur
EP0085889B1 (fr) Machine à piston rotatif à deux ou plusieurs étages
DE112011100746T5 (de) Verbindungsstruktur zwischen hohler abtriebswelle und angetriebener welle und drehzahluntersetzungsgetriebe
DE1813335B2 (de) Mehrstufiger Turboverdichter
DE4239138A1 (de) Verdichteranlage
EP2839133B1 (fr) Support de turbocompound pour relier un système de turbocompound à un moteur à combustion interne
EP3299630A1 (fr) Système de compresseur
EP3491272B1 (fr) Dispositif d'entrainement comportant une boîte de superposition
EP3236076B1 (fr) Système de turbomachine
DE112019006213T5 (de) Hybrid-Reduzierersystem
EP1478080B1 (fr) Turbomachine
DE102016216665A1 (de) Axialströmungskraftmaschine mit drehendem Stator und Rotor
DE102015220167A1 (de) Abgasturbolader für eine Brennkraftmaschine
DE102017103695A1 (de) Antriebsvorrichtung mit Überlagerungsgetriebe

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

AX Request for extension of the european patent

Extension state: BA ME

RAP1 Party data changed (applicant data changed or rights of an application transferred)

Owner name: SIEMENS AKTIENGESELLSCHAFT

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE APPLICATION IS DEEMED TO BE WITHDRAWN

18D Application deemed to be withdrawn

Effective date: 20170622