EP1067291A1 - Transmission and centrifugal compressor - Google Patents

Transmission and centrifugal compressor Download PDF

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Publication number
EP1067291A1
EP1067291A1 EP99250222A EP99250222A EP1067291A1 EP 1067291 A1 EP1067291 A1 EP 1067291A1 EP 99250222 A EP99250222 A EP 99250222A EP 99250222 A EP99250222 A EP 99250222A EP 1067291 A1 EP1067291 A1 EP 1067291A1
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Prior art keywords
gear
main drive
pinion shafts
compressor
driven
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EP99250222A
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German (de)
French (fr)
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EP1067291B1 (en
Inventor
Heinrich J. Dr.-Ing. Prümper
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Voith Turbo BHS Getriebe GmbH
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PRUEMPER HEINRICH J DR ING
Pruemper Heinrich J Dr-Ing
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Priority to EP99250222A priority Critical patent/EP1067291B1/en
Priority to DE59909914T priority patent/DE59909914D1/en
Priority to AT99250222T priority patent/ATE270753T1/en
Publication of EP1067291A1 publication Critical patent/EP1067291A1/en
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    • 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

Definitions

  • the invention relates to a multi-stage single-stage double gear driven turbo compressor, a so-called geared turbo compressor with the features of the preamble of Claim 1.
  • a known turbo compressor of the generic type Art (DE-PS 9 74 418, DE-OS 21 15 331, Dubbel paperback for mechanical engineering 14. Edition, 1981, pages 920 - 921) has four compression stages on, whose impellers in pairs two pinion shafts arranged and via a central one Drive gear of a single-stage gear are driven.
  • DE-OS 37 07 992 is a geared turbo compressor known, between the drive shaft and the one that carries the compressor impellers Pinion shaft arranged an intermediate gear is.
  • This intermediate gear serves as a lock-up a large center distance between the Drive shaft and the pinion shaft so that at small Flywheels a low speed in one very high speed can be translated.
  • the US-PS 23 13 205 shows a transmission for one Turbo compressor, the two arranged on a shaft nete gears of different diameters contains, via which the drive shaft with the compressor shaft connected is.
  • DE 40 03 482 C2 and EP 0 440 902 B1 show a geared turbo compressor with a two-stage gearbox that has a double idler gear contains, with a smaller gear and a slightly larger gear together a wave shrunk and thereby one Unit connected, the smaller one Gear has the larger tooth module and engages with the main drive gear and the larger gear a much smaller one Has tooth module and the pinion shafts 3, 4 and 5 drives.
  • the pinion shafts 1 and 2 are with and the main drive gear driven by this.
  • the level of the achievable efficiency of a turbocompressor depends on whether the dimensionless "specific speed" a of each individual compressor stage can be kept in the optimal range despite strong volume flow changes due to the compression from compressor stage to compressor stage.
  • each one Compressor stage is according to the written relationship from the secondary Speed, the inlet volume flow and depending on the size Y, where Y from the gas data, the inlet temperature and especially from that Pressure ratio the compressor stage becomes.
  • Step pressure ratio only a little or can be constant, the inlet volume flow changes through the compression strong from level to level.
  • the speed must increase from step Level or at the latest after two levels increase.
  • the intermediate gear requires a separate bearing (axially and radially), the journals rotating at approximately twice the drive speed (or more).
  • the input and output tooth forces add up on an idler gear and increase the bearing load.
  • the relatively high peripheral speeds generate considerable additional mechanical losses.
  • the gear of the double idler gear meshing with the main drive gear has the same peripheral speed as the main drive gear.
  • the second with the smaller tooth module has a higher peripheral speed and, like the bearing, generates additional mechanical losses.
  • the construction work for the gearbox, including the oil supply for the idler gear, is considerably higher.
  • the invention has for its object to build a transmission turbocompressor for high pressure ratios with optimal efficiencies or combination turbo compressors with widely differing volume flows with optimal efficiencies without the use of a double intermediate gear according to DE 40 03 482 C2 and EP 0 440 902 B1.
  • FIG.1 to FIG.5 An embodiment of the invention is shown in the drawings FIG.1 to FIG.5 and is explained in more detail below:
  • the drawings represent an integral gear for a multi-stage turbocompressor or for a combination turbocompressor.
  • a main drive gear (2) and a shrunk-on secondary gear (3) are driven via the drive shaft (1).
  • the root circle of the secondary gear (3) is larger than the tip circle of the main drive gear (2).
  • the tooth module of the secondary gear (3) is significantly smaller than the tooth module of the main drive gear (2), so the number of teeth of (3) is significantly larger than the number of teeth of (2).
  • the pinion shafts (4) and (5) mesh with the main drive gear (2), the pinion shafts (6) and (7) mesh with the secondary ring gear (3).
  • the free ends of the pinion shafts (4) to (7) can be equipped, for example, with the impellers of a seven- or eight-stage geared turbocompressor, with all the laurels working in the optimal range of their specific speed. Such a turbocompressor has an optimal efficiency.
  • the pinion shafts (4) and (5) can be equipped with the impellers of a three- or four-stage basic compressor, while the pinion shafts (6) and (7) carry the impellers of a second independent compressor, the volume flow of the second compressor being less than that of the basic compressor.
  • Combinations e.g. Basic compressor three or four stages, first additional compressor two-stage, second additional compressor two-stage.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Gear Transmission (AREA)
  • Supercharger (AREA)
  • Electron Tubes For Measurement (AREA)
  • Eye Examination Apparatus (AREA)

Abstract

Multi-stage turbo-compressor has an integrated gear with central drive double gearwheels. The running wheels of the compressor stages are arranged on the ends of pinion shafts (4-7). The gear has two drive gearwheels connected by a shaft (1) to form a unit, a main drive gearwheel (2) and a secondary toothed crown (3). The secondary toothed crown has a smaller tooth module than the main gearwheel. The foot circle of the secondary toothed crown is equal to or greater than the head circle of the main drive gearwheel. The first pinion shafts (4,5) are driven by the main drive gearwheel and have the same tooth module as it. The second pinion shafts (6,7) are engaged with the secondary toothed crown, have the same smaller tooth module and are driven by it.

Description

Die Erfindung betrifft einen mehrstufigen über einstufiges Doppelgetriebe angetriebenen Turboverdichter, einen sogenannten Getriebe-Turboverdichter mit den Merkmalen des Oberbegriffes des Patentanspruches 1.The invention relates to a multi-stage single-stage double gear driven turbo compressor, a so-called geared turbo compressor with the features of the preamble of Claim 1.

Ein bekannter Turboverdichter der gattungsgemäßen Art (DE-PS 9 74 418, DE-OS 21 15 331, Dubbel Taschenbuch für den Maschinenbau 14. Auflage, 1981, Seiten 920 - 921) weist vier Verdichterstufen auf, deren Laufräder paarweise auf zwei Ritzelwellen angeordnet und über ein zentrales Antriebszahnrad eines einstufigen Getriebes angetrieben sind.A known turbo compressor of the generic type Art (DE-PS 9 74 418, DE-OS 21 15 331, Dubbel paperback for mechanical engineering 14. Edition, 1981, pages 920 - 921) has four compression stages on, whose impellers in pairs two pinion shafts arranged and via a central one Drive gear of a single-stage gear are driven.

Aus der DE-OS 37 07 992 ist ein Getriebe-Turboverdichter bekannt, bei dem zwischen der Antriebswelle und der die Verdichterlaufräder tragenden Ritzelwelle ein Zwischenzahnrad angeordnet ist. Dieses Zwischenzahnrad dient der Überbrückung eines großen Achsabstandes zwischen der Antriebswelle und der Ritzelwelle, so daß bei kleinen Schwungmassen eine niedrige Drehzahl in eine sehr hohe Drehzahl übersetzt werden kann.DE-OS 37 07 992 is a geared turbo compressor known, between the drive shaft and the one that carries the compressor impellers Pinion shaft arranged an intermediate gear is. This intermediate gear serves as a lock-up a large center distance between the Drive shaft and the pinion shaft so that at small Flywheels a low speed in one very high speed can be translated.

Die US-PS 23 13 205 zeigt ein Getriebe für einen Turboverdichter, das zwei auf einer Welle angeord nete Zahnräder unterschiedlichen Durchmessers enthält, über die die Antriebswelle mit der Verdichterwelle verbunden ist.The US-PS 23 13 205 shows a transmission for one Turbo compressor, the two arranged on a shaft nete gears of different diameters contains, via which the drive shaft with the compressor shaft connected is.

Die DE 40 03 482 C2 und die EP 0 440 902 B1 zeigen einen Getriebeturboverdichter mit einem zweistufigen Getriebe, der ein Doppelzwischenzahnrad enthält, wobei ein kleineres Zahnrad und ein etwas größeres Zahnrad gemeinsam auf eine Welle aufgeschrumpft und dadurch zu einer Einheit verbunden werden, wobei das kleinere Zahnrad den größeren Zahnmodul aufweist und mit dem Hauptantriebszahnrad in Eingriff steht und das größere Zahnrad einen wesentlich kleineren Zahnmodul aufweist und die Ritzelwellen 3, 4 und 5 antreibt. Die Ritzelwellen 1 und 2 stehen mit dem Hauptantriebszahnrad in Eingriff und werden von diesem angetrieben.DE 40 03 482 C2 and EP 0 440 902 B1 show a geared turbo compressor with a two-stage gearbox that has a double idler gear contains, with a smaller gear and a slightly larger gear together a wave shrunk and thereby one Unit connected, the smaller one Gear has the larger tooth module and engages with the main drive gear and the larger gear a much smaller one Has tooth module and the pinion shafts 3, 4 and 5 drives. The pinion shafts 1 and 2 are with and the main drive gear driven by this.

Die Höhe des erreichbaren Wirkungsgrades eines Turboverdichters hängt davon ab, ob die dimensionslose "Spezifische Drehzahl" a jeder einzelnen Verdichterstufe im Optimalbereich gehalten werden kann trotz starker Volumenstromänderungen infolge der Verdichtung von Verdichterstufe zu Verdichterstufe.

Figure 00010001
Figure 00010002
The level of the achievable efficiency of a turbocompressor depends on whether the dimensionless "specific speed" a of each individual compressor stage can be kept in the optimal range despite strong volume flow changes due to the compression from compressor stage to compressor stage.
Figure 00010001
Figure 00010002

Die spezifische Drehzahl jeder einzelnen Verdichterstufe ist gemäß der angeschriebenen Beziehung von der sekundlichen Drehzahl, dem Eintrittsvolumenstrom und der Größe Y abhängig, wobei Y aus den Gasdaten, der Eintrittstemperatur und vor allem aus dem Druckverhältnis der Verdichterstufe berechnet wird. In der Regel verändert sich das Stufendruckverhältnis nur wenig oder kann konstant sein, der Eintrittsvolumenstrom verändert sich durch die Verdichtung von Stufe zu Stufe stark. Um die spezifische Drehzahl und damit den Stufenwirkungsgrad im Optimalbereich zu halten, muß die Drehzahl von Stufe zu Stufe oder spätestens nach zwei Stufen erhöht werden.The specific speed of each one Compressor stage is according to the written relationship from the secondary Speed, the inlet volume flow and depending on the size Y, where Y from the gas data, the inlet temperature and especially from that Pressure ratio the compressor stage becomes. Usually this changes Step pressure ratio only a little or can be constant, the inlet volume flow changes through the compression strong from level to level. To the specific speed and thus the step efficiency in the optimal range hold, the speed must increase from step Level or at the latest after two levels increase.

Steigende Stufendruckverhältnisse sind untrennbar mit steigenden Strömungsgeschwindigkeiten gekoppelt. Bei Annäherung an die Schallgeschwindigkeit nehmen die Srömungsverluste stark zu und somit der Wirkungsgrad ab, die Stufendruckverhältnisse sind daher begrenzt. Turboverdichter für hohe Druckverhältnisse erfordern entsprechend viele Verdichterstufen. Für ein Druckverhältnis von Pa/Pe = 60 sind z.B. sechs bis sieben Verdichterstufen, für Pa/Pe =90 mindestens acht Verdichterstufen und Druckverhältnisse Pa/Pe = 180-200 mindestens zehn Verdichterstufen erforderlich.Rising pressure ratios are inseparable from increasing flow velocities coupled. When approaching take on the speed of sound the flow losses increase sharply and hence the efficiency, the step pressure ratios are therefore limited. Turbo compressor for high pressure conditions require a corresponding number of compressor stages. For a pressure ratio of Pa / Pe = 60 are e.g. six to seven Compressor stages, for Pa / Pe = 90 at least eight compressor stages and pressure ratios Pa / Pe = 180-200 at least ten compressor stages required.

In Turboverdichtem dieser Gattung haben die ersten Stufen mäßige Drehzahlen, während die letzten Stufen sehr hohe Drehzahlen erfordern. In this type of turbocompressor the first stages moderate speeds, while the last levels are very high Speeds require.

Es ist also zwangsläufig, daß neben normalen Übersetzungsverhältnissen sehr große Übersetzungsverhältnisse in einem Getriebe realisiert werden müssen. Ähnliche Verhältnisse liegen vor, wenn zwei oder gar drei Turboverdichter zu einer Einheit zu sogenannten Kombiverdichtern zusammengefaßt werden. Da alle in der Regel verschieden große Volumenströme verdichten, welche möglicherweise erheblich voneinander abweichen, ergibt sich auch hier die Notwendigkeit neben normalen Überstzungsverhältnissen große Übersetzungen in ein und demselben Getriebe technisch zu realisieren.So it is inevitable that besides normal Very high gear ratios Gear ratios realized in a gearbox Need to become. Similar conditions exist before when two or even three turbo compressors too one unit for so-called combi compressors be summarized. Since all usually compress different volume flows, which may differ significantly deviate, there is also a need here in addition to normal translation ratios large translations in one and the same Technically implement gearbox.

In DE 40 03 482 C2 und EP 0 440 902 B1 werden Getriebe-Turboverdichter beschrieben, welche erfindungsgemäß das geschilderte Problem durch Einbau eines Doppel-Zwischenzahnrades lösen, wobei die beiden zu einer Einheit zusammengefaßten Zahnräder stark verschiedene Zahnmodule aufweisen. Das Getriebe ist dadurch zwangsweise zweistufig.DE 40 03 482 C2 and EP 0 440 902 B1 describe transmission turbo compressors, which according to the invention the problem described solve by installing a double intermediate gear, the two gears combined into one unit are very different Have tooth modules. The gear is therefore compulsory two-stage.

Diese Lösung enthält folgende Nachteile:
Das Zwischenzahnrad erfordert eine separate Lagerung (axial u. radial), wobei die Lagerzapfen mit etwa der doppelten Antriebsdrehzahl (oder mehr) umlaufen. Außerdem addieren sich bei einem Zwischenrad die An- und Abtriebszahnkräfte und verstärken die Lagerbelastung. Die relativ hohen Umfangsgeschwindigkeiten erzeugen erhebliche mechanische Zusatzverluste.This solution has the following disadvantages:
The intermediate gear requires a separate bearing (axially and radially), the journals rotating at approximately twice the drive speed (or more). In addition, the input and output tooth forces add up on an idler gear and increase the bearing load. The relatively high peripheral speeds generate considerable additional mechanical losses.

Das mit dem Hauptantriebszahnrad in Eingriff stehende Zahnrad des Doppelzwischenrades hat die gleiche Umfangsgeschwindigkeit wie das Hauptantriebszahnrad. Das zweite mit dem kleineren Zahnmodul hat eine höhere Umfangsgeschwindigkeit und erzeugt wie die Lagerung zusätzliche mechanische Verluste. Der Bauaufwand für das Getriebegehäuse, inklusive der Ölzuführung für das Zwischenzahnrad, ist erheblich höher.The gear of the double idler gear meshing with the main drive gear has the same peripheral speed as the main drive gear. The second with the smaller tooth module has a higher peripheral speed and, like the bearing, generates additional mechanical losses. The construction work for the gearbox, including the oil supply for the idler gear, is considerably higher.

Der Erfindung liegt die Aufgabe zugrunde, einen Getriebe-Turboverdichter für hohe Druckverhältnisse mit optimalen Wirkungsgraden oder Kombi-Turboverdichter mit stark differierenden Volumenströmen mit optimalen Wirkungsgraden zu bauen ohne die Verwendung eines Doppel-Zwischenzahnrades gemäß DE 40 03 482 C2 und EP 0 440 902 B1.The invention has for its object to build a transmission turbocompressor for high pressure ratios with optimal efficiencies or combination turbo compressors with widely differing volume flows with optimal efficiencies without the use of a double intermediate gear according to DE 40 03 482 C2 and EP 0 440 902 B1.

Diese Aufgabe wird bei einem gattungsgemäßen Turboverdichter erfindungsgemäß durch die kennzeichnenden Merkmale des Patentanspruchs 1 gelöst.This object is achieved according to the invention in a generic turbocompressor by the characterizing features of patent claim 1.

Durch Aufschrumpfen eines Sekundärzahnkranzes (3) auf eine seitlich angeordnete zylindrische Fläche des Hauptantriebszahnrades (2), wobei der Sekundärzahnkranz einen wesentlich kleineren Zahnmodul aufweist als das Hauptantriebszahnrad, wodurch dessen Zähnezahl erhöht wird, wird ein integrales Getriebe für Turboverdichter geschaffen, welches neben mäßigen Drehzahlen für die ersten Verdichterstufen gleichzeitig sehr hohe Drehzahlen für die kleineren Verdichterstufen realisiert.By shrinking a secondary ring gear (3) onto a side one cylindrical surface of the main drive gear (2), the secondary ring gear having a much smaller tooth module than the main drive gear, which increases the number of teeth, an integral gear for turbocompressors is created which, in addition to moderate speeds for the first compressor stages, very high speeds for the smaller compressor stages realized.

Ein Ausführungsbeispiel der Erfindung ist in den Zeichnungen FIG.1 bis FIG.5 dargestellt und wird im folgenden näher erläutert:
Die Zeichnungen stellen ein integrales Geriebe für einen mehrstufigen Turboverdichter oder für eine Kombi-Turboverdichter dar. Über die Antriebswelle (1) werden ein Hauptantriebszahnrad (2) und ein aufgeschrumpftes Sekundärzahnrad (3) angetrieben. Der Fußkreis des Sekundärzahnrades (3) ist größer als der Kopfkreis des Hauptantriebszahnrades (2). Der Zahnmodul des Sekundärzahnrades (3) ist wesentlich kleiner als der Zahnmodul des Hauptantriebszahnrades (2), dementsprechend ist die Zähnezahl von (3) wesentlich größer als die Zähnezahl von (2). Die Ritzelwellen (4) und (5) stehen mit dem Hauptantriebszahnrad (2) im Eingriff, die Ritzelwellen (6) und (7) kämmen mit dem Sekundärzahnkranz (3). Dadurch ist es möglich, die Ritzelwellen (6) und (7) mit sehr viel höheren Drehzahlen anzutreiben als die Ritzelwellen (4) und (5). Die freien Enden der Ritzelwellen (4) bis (7) können z.B. mit den Laufrädern eines sieben- oder achtstufigen Getriebeturboverdichters bestückt werden, wobei alle Lauräder im optimalen Bereich ihrer spezifischen Drehzahl arbeiten. Ein solcher Turboverdichter weist einen optimalen Wirkungsgrad auf. Ebenso können die Ritzelwellen (4) und (5) mit den Laufrädern eines drei- oder vierstufigen Basisverdichters besetzt sein, während die Ritzelwellen (6) und (7) die Laufräder eines zweiten unabhängigen Verdichters tragen, wobei der Volumenstrom des zweiten Verdichters kleiner ist als der des Basisverdichters. An embodiment of the invention is shown in the drawings FIG.1 to FIG.5 and is explained in more detail below:
The drawings represent an integral gear for a multi-stage turbocompressor or for a combination turbocompressor. A main drive gear (2) and a shrunk-on secondary gear (3) are driven via the drive shaft (1). The root circle of the secondary gear (3) is larger than the tip circle of the main drive gear (2). The tooth module of the secondary gear (3) is significantly smaller than the tooth module of the main drive gear (2), so the number of teeth of (3) is significantly larger than the number of teeth of (2). The pinion shafts (4) and (5) mesh with the main drive gear (2), the pinion shafts (6) and (7) mesh with the secondary ring gear (3). This makes it possible to drive the pinion shafts (6) and (7) at much higher speeds than the pinion shafts (4) and (5). The free ends of the pinion shafts (4) to (7) can be equipped, for example, with the impellers of a seven- or eight-stage geared turbocompressor, with all the laurels working in the optimal range of their specific speed. Such a turbocompressor has an optimal efficiency. Likewise, the pinion shafts (4) and (5) can be equipped with the impellers of a three- or four-stage basic compressor, while the pinion shafts (6) and (7) carry the impellers of a second independent compressor, the volume flow of the second compressor being less than that of the basic compressor.

Es ergeben sich logischerweise weitere Kombinationen, z.B. Basisverdichter drei- oder vierstufig, erster Zusatzverdichter zweistufig, zweiter Zusatzverdichter zweistufig.There are logically more Combinations, e.g. Basic compressor three or four stages, first additional compressor two-stage, second additional compressor two-stage.

Basisverdichter zweistufig, erster Zusatzverdichter zweistufig, zweiter Zusatzverdichter drei- oder vierstufig.Basic compressor in two stages, first Additional compressor in two stages, second additional compressor three or four stages.

Alle denkbaren Kombinationen sind zulässig, sofern die spezifischen Drehzahlen der Verdichterstufen im Optimalbereich gehalten werden können. Kompromisse sind denbkbar, da die Herstellkosten für einen Kombiverdichter geringer sind als für Einzelverdichter.All conceivable combinations are permissible, provided the specific speeds the compressor stages in the optimal range can be held. Compromise are conceivable since the manufacturing costs for a combi compressor are less than for single compressors.

Claims (4)

Mehrstufiger Turboverdichter mit integriertem, ein zentrales Antriebsdoppelzahnrad aufweisenden Getriebe, bei dem die Laufräder der Verdichterstufen auf den Enden von Ritzelwellen (4, 5, 6, 7) angeordnet sind, dadurch gekennzeichnet, daß das Getriebe zwei durch eine Antriebswelle (1) zu einer Einheit verbundene Antriebszahnräder aufweist, einem Hauptantriebszahnrad (2) und einem Sekundärzahnkranz (3), wobei der Sekundärzahnkranz (3) einen kleineren Zahnmodul als das Hauptantriebszahnrad (2) aufweist, und der Fußkreis des Sekundärzahnkranzes (3) gleich oder größer als der Kopfkreis des Hauptantriebszahnrades ist, und daß die ersten Ritzelwellen (4, 5) durch das Hauptantriebszahnrad angetrieben sind und den gleichen Zahnmodul wie dieses aufweisen, die weiteren Ritzelwellen (6, 7) mit dem Sekundärzahnkranz (3) in Eingriff stehen, den gleichen kleineren Zahnmodul wie (3) aufweisen und von diesem angetrieben sind.Multi-stage turbocompressor with integrated, a central drive double gear having gear, in which the wheels of the compressor stages on the ends of Pinion shafts (4, 5, 6, 7) are arranged, characterized in that the transmission two by one drive shaft (1) to one Unit connected drive gears has a main drive gear (2) and a secondary ring gear (3), wherein the secondary ring gear (3) has a smaller one Tooth module as the main drive gear (2), and the root circle of the secondary ring gear (3) equal to or greater than the tip circle of the main drive gear and that the first pinion shafts (4, 5) driven by the main drive gear and the same tooth module as have this, the further pinion shafts (6, 7) with the secondary ring gear (3) in Stand by, the same smaller Have tooth module as (3) and from this are driven. Turboverdichter nach Anspruch 1., dadurch gekennzeichnet, daß mehr als zwei Ritzelwellen mit dem Hauptantriebszahnrad (2) in Eingriff stehen und von diesem angetrieben sind.Turbo compressor according to claim 1, characterized characterized that more than two pinion shafts with the main drive gear (2) in Stand by and driven by this are. Turboverdichter nach Anspruch 1., dadurch gekennzeichnet, daß mehr als zwei Ritzelwellen mit dem Sekundärzahnkranz (3) in Eingriff stehen und von diesem angetrieben sind.Turbo compressor according to claim 1, characterized characterized that more than two pinion shafts with the secondary ring gear (3) in Stand by and driven by this are. Turboverdichter nach Anspruch 1., dadurch gekennzeichnt, daß das Antriebsdoppelzahnrad (1, 2, 3) symmetrisch als Tripelzahnrad ausgebildet ist, wobei der Sekundärzahnkranz (3) zweiteilig ausgeführt ist und auf beiden Seiten des Hauptantriebszahnrades aufgeschrumpft ist.Turbo compressor according to claim 1, characterized marked that the drive double gear (1, 2, 3) symmetrical as a triple gear is formed, the secondary ring gear (3) is made in two parts and on both sides of the main drive gear has shrunk.
EP99250222A 1999-07-05 1999-07-05 Transmission and centrifugal compressor Expired - Lifetime EP1067291B1 (en)

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EP99250222A EP1067291B1 (en) 1999-07-05 1999-07-05 Transmission and centrifugal compressor
DE59909914T DE59909914D1 (en) 1999-07-05 1999-07-05 Geared turbocompressor
AT99250222T ATE270753T1 (en) 1999-07-05 1999-07-05 TRANSMISSION TURB COMPRESSOR

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* Cited by examiner, † Cited by third party
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DE102011003525A1 (en) * 2011-02-02 2012-08-02 Siemens Aktiengesellschaft Stepped parting line on a gearbox
WO2013021664A1 (en) * 2011-08-05 2013-02-14 三菱重工コンプレッサ株式会社 Centrifugal compressor
CN104005966A (en) * 2014-05-29 2014-08-27 安徽银龙泵阀股份有限公司 Multi-spindle pump core capable of rotating by means of star gear principle

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DE102014225136A1 (en) 2014-12-08 2016-06-09 Siemens Aktiengesellschaft Transmission compressor, arrangement with a drive and a gear compressor
JP2021156281A (en) * 2021-02-01 2021-10-07 三菱重工コンプレッサ株式会社 Geared compressor and method for designing geared compressor

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Cited By (11)

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DE102011003525A1 (en) * 2011-02-02 2012-08-02 Siemens Aktiengesellschaft Stepped parting line on a gearbox
WO2012104153A1 (en) 2011-02-02 2012-08-09 Siemens Aktiengesellschaft Stepped parting joint on a transmission housing of a fluid machine
CN103339383A (en) * 2011-02-02 2013-10-02 西门子公司 Stepped parting joint on a transmission housing of a fluid machine
EP2649321A1 (en) 2011-02-02 2013-10-16 Siemens Aktiengesellschaft Stepped parting joint on a transmission housing of a fluid machine
US20130315707A1 (en) * 2011-02-02 2013-11-28 Siemens Aktiengesellschaft Stepped parting joint on a transmission housing of a fluid machine
CN103339383B (en) * 2011-02-02 2016-03-23 西门子公司 The joining portion of the stepped shape on the driving mechanism housing of fluid machinery
US9631623B2 (en) 2011-02-02 2017-04-25 Siemens Aktiengesellschaft Stepped parting joint on a transmission housing of a fluid machine
WO2013021664A1 (en) * 2011-08-05 2013-02-14 三菱重工コンプレッサ株式会社 Centrifugal compressor
JP2013036375A (en) * 2011-08-05 2013-02-21 Mitsubishi Heavy Industries Compressor Corp Centrifugal compressor
US9714658B2 (en) 2011-08-05 2017-07-25 Mitsubishi Heavy Industries Compressor Corporation Centrifugal compressor
CN104005966A (en) * 2014-05-29 2014-08-27 安徽银龙泵阀股份有限公司 Multi-spindle pump core capable of rotating by means of star gear principle

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ATE270753T1 (en) 2004-07-15
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