EP1067291A1 - Getriebe-Turboverdichter - Google Patents
Getriebe-Turboverdichter Download PDFInfo
- 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
- Authority
- EP
- European Patent Office
- Prior art keywords
- gear
- main drive
- pinion shafts
- compressor
- driven
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
- 230000005540 biological transmission Effects 0.000 title claims description 5
- 230000006835 compression Effects 0.000 description 3
- 238000007906 compression Methods 0.000 description 3
- 230000002093 peripheral effect Effects 0.000 description 3
- 230000014616 translation Effects 0.000 description 2
- 238000013519 translation Methods 0.000 description 2
- 241000218195 Lauraceae Species 0.000 description 1
- 235000017858 Laurus nobilis Nutrition 0.000 description 1
- 235000005212 Terminalia tomentosa Nutrition 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 238000011089 mechanical engineering Methods 0.000 description 1
- 230000000630 rising effect Effects 0.000 description 1
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
- F04D25/02—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.
Abstract
Description
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.
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.
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.
- Turboverdichter nach Anspruch 1., dadurch gekennzeichnet, daß mehr als zwei Ritzelwellen mit dem Hauptantriebszahnrad (2) in Eingriff stehen und von diesem angetrieben sind.
- Turboverdichter nach Anspruch 1., dadurch gekennzeichnet, daß mehr als zwei Ritzelwellen mit dem Sekundärzahnkranz (3) in Eingriff stehen und von diesem angetrieben sind.
- 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.
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
AT99250222T ATE270753T1 (de) | 1999-07-05 | 1999-07-05 | Getriebe-turboverdichter |
DE59909914T DE59909914D1 (de) | 1999-07-05 | 1999-07-05 | Getriebe-Turboverdichter |
EP99250222A EP1067291B1 (de) | 1999-07-05 | 1999-07-05 | Getriebe-Turboverdichter |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP99250222A EP1067291B1 (de) | 1999-07-05 | 1999-07-05 | Getriebe-Turboverdichter |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1067291A1 true EP1067291A1 (de) | 2001-01-10 |
EP1067291B1 EP1067291B1 (de) | 2004-07-07 |
Family
ID=8241150
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP99250222A Expired - Lifetime EP1067291B1 (de) | 1999-07-05 | 1999-07-05 | Getriebe-Turboverdichter |
Country Status (3)
Country | Link |
---|---|
EP (1) | EP1067291B1 (de) |
AT (1) | ATE270753T1 (de) |
DE (1) | DE59909914D1 (de) |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102011003525A1 (de) * | 2011-02-02 | 2012-08-02 | Siemens Aktiengesellschaft | Gestufte Teilfuge an einem Getriebegehäuse |
WO2013021664A1 (ja) * | 2011-08-05 | 2013-02-14 | 三菱重工コンプレッサ株式会社 | 遠心圧縮機 |
CN104005966A (zh) * | 2014-05-29 | 2014-08-27 | 安徽银龙泵阀股份有限公司 | 一种利用星级齿轮原理旋转的多转轴泵芯 |
Families Citing this family (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102013208564A1 (de) | 2013-05-08 | 2014-11-13 | Voith Patent Gmbh | Getriebe und Getriebeverdichteranlage |
DE102014225136A1 (de) | 2014-12-08 | 2016-06-09 | Siemens Aktiengesellschaft | Getriebeverdichter, Anordnung mit einem Antrieb und einem Getriebeverdichter |
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 |
Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE974418C (de) * | 1948-10-02 | 1960-12-15 | Demag Ag | Kreiselverdichter mit mindestens vier hintereinander-geschalteten Stufen |
DE2115331A1 (de) * | 1971-03-30 | 1972-10-12 | Demag Ag | Mehrstufiger radialer Turbokompres sor |
EP0440902A1 (de) * | 1990-02-06 | 1991-08-14 | Deutsche Babcock- Borsig Aktiengesellschaft | Getriebe-Turboverdichter |
DE9201858U1 (de) * | 1992-02-11 | 1992-04-02 | Mannesmann Ag, 4000 Duesseldorf, De |
-
1999
- 1999-07-05 AT AT99250222T patent/ATE270753T1/de not_active IP Right Cessation
- 1999-07-05 EP EP99250222A patent/EP1067291B1/de not_active Expired - Lifetime
- 1999-07-05 DE DE59909914T patent/DE59909914D1/de not_active Expired - Lifetime
Patent Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE974418C (de) * | 1948-10-02 | 1960-12-15 | Demag Ag | Kreiselverdichter mit mindestens vier hintereinander-geschalteten Stufen |
DE2115331A1 (de) * | 1971-03-30 | 1972-10-12 | Demag Ag | Mehrstufiger radialer Turbokompres sor |
EP0440902A1 (de) * | 1990-02-06 | 1991-08-14 | Deutsche Babcock- Borsig Aktiengesellschaft | Getriebe-Turboverdichter |
DE9201858U1 (de) * | 1992-02-11 | 1992-04-02 | Mannesmann Ag, 4000 Duesseldorf, De |
Cited By (11)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102011003525A1 (de) * | 2011-02-02 | 2012-08-02 | Siemens Aktiengesellschaft | Gestufte Teilfuge an einem Getriebegehäuse |
WO2012104153A1 (de) | 2011-02-02 | 2012-08-09 | Siemens Aktiengesellschaft | Gestufte teilfuge an einem getriebegehäuse einer fluidmaschine |
CN103339383A (zh) * | 2011-02-02 | 2013-10-02 | 西门子公司 | 流体机械的传动机构壳体上的台阶形的接合部 |
EP2649321A1 (de) | 2011-02-02 | 2013-10-16 | Siemens Aktiengesellschaft | Gestufte teilfuge an einem getriebegehäuse einer fluidmaschine |
US20130315707A1 (en) * | 2011-02-02 | 2013-11-28 | Siemens Aktiengesellschaft | Stepped parting joint on a transmission housing of a fluid machine |
CN103339383B (zh) * | 2011-02-02 | 2016-03-23 | 西门子公司 | 流体机械的传动机构壳体上的台阶形的接合部 |
US9631623B2 (en) | 2011-02-02 | 2017-04-25 | Siemens Aktiengesellschaft | Stepped parting joint on a transmission housing of a fluid machine |
WO2013021664A1 (ja) * | 2011-08-05 | 2013-02-14 | 三菱重工コンプレッサ株式会社 | 遠心圧縮機 |
JP2013036375A (ja) * | 2011-08-05 | 2013-02-21 | Mitsubishi Heavy Industries Compressor Corp | 遠心圧縮機 |
US9714658B2 (en) | 2011-08-05 | 2017-07-25 | Mitsubishi Heavy Industries Compressor Corporation | Centrifugal compressor |
CN104005966A (zh) * | 2014-05-29 | 2014-08-27 | 安徽银龙泵阀股份有限公司 | 一种利用星级齿轮原理旋转的多转轴泵芯 |
Also Published As
Publication number | Publication date |
---|---|
ATE270753T1 (de) | 2004-07-15 |
DE59909914D1 (de) | 2004-08-12 |
EP1067291B1 (de) | 2004-07-07 |
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