EP1957798B1 - Schraubenkompressor - Google Patents
Schraubenkompressor Download PDFInfo
- Publication number
- EP1957798B1 EP1957798B1 EP06762002A EP06762002A EP1957798B1 EP 1957798 B1 EP1957798 B1 EP 1957798B1 EP 06762002 A EP06762002 A EP 06762002A EP 06762002 A EP06762002 A EP 06762002A EP 1957798 B1 EP1957798 B1 EP 1957798B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- rotor
- profile
- screw compressor
- rotors
- ribs
- 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.)
- Active
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
- F04C18/082—Details specially related to intermeshing engagement type pumps
- F04C18/084—Toothed wheels
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
- F04C18/12—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
- F04C18/14—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
- F04C18/16—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw type
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
- F04C23/001—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids of similar working principle
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/04—Heating; Cooling; Heat insulation
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2220/00—Application
- F04C2220/40—Pumps with means for venting areas other than the working chamber, e.g. bearings, gear chambers, shaft seals
Definitions
- the invention relates to a screw compressor with two in a rotor housing axially parallel rotatably mounted screw rotors, each of which has a profile section with helically extending ribs and grooves.
- the rotors mesh and seal with each other with their ribs and grooves, and in operation, gas volumes trapped between them and the rotor housing are conveyed and compressed.
- Such a screw compressor is from the US3986801 known, which is considered as the closest prior art.
- the present invention aims to provide a screw compressor which is suitable for the compression of gas to very high pressures, typically in the range of 30 to 50 bar, and in particular as the last stage of a multi-stage, in particular three-stage Compressor unit can be operated.
- the rotors are subjected to strong transverse axial forces acting through the gas volume trapped between them and the housing under high pressure, which act to deflect the rotors. This can lead to a deterioration of the seal between the rotors and thus to a loss of efficiency.
- the radial gap between the rotors and the rotor housing can not be made as small as would be desirable to achieve good sealing and high efficiency.
- the object of the invention is therefore to provide a screw compressor, which is particularly suitable for operation at high compression pressures.
- the in FIG. 1 screw compressor shown as an exemplary embodiment has a rotor housing 1 shown in section, in which two rotors 3 and 5 are mounted rotatably parallel axes.
- the axes of rotation of the rotors 3, 5 lie in a common vertical plane, which is also the cutting plane for the representation of the rotor housing 1.
- Each rotor has a profile section 7 or 9, which has a profile with helically extending ribs or grooves, wherein the ribs and grooves of the two profile sections 7, 9 mesh with each other.
- At the profile sections 7, 9 close to shaft journals 7a, 7b, 9a, 9b, with their peripheral surface sealing rings 11 cooperate to seal the rotor in the rotor housing 1.
- the shaft journals 7a, 7b, 9a, 9b are also rotatably supported by bearings 13, 15 in the rotor housing 1.
- the in FIG. 1 upper rotor 3 is the main rotor and has at its in FIG. 1 left end of an extension 7c of its shaft journal, which is intended to receive a drive gear (not shown) which meshes with a corresponding gear of a drive gear (not shown) to drive the rotor 3 for rotation.
- the screw compressor described is preferably dry-running, that is, the compressor room, no oil for lubrication, cooling or sealing is supplied.
- the rotor profiles engage without contact and yet sealingly into each other. This is advantageous for all applications in which it depends on complete freedom from oil of the compressed gas. Oil is only outside the compressor room, d. H. outside the area sealed by the seals 11, e.g. B. for lubrication of the (not shown) drive gear, the bearing 13, 15 and the constant velocity gear 17, 19 fed.
- FIG. 2 are the two rotors 3, 5 of the screw compressor of FIG. 1 shown separately in perspective.
- the rotor 3 which is the main rotor, has a profile section 7 whose profile is formed by six helically extending ribs 7 '.
- the sum of the numbers of helical ribs 7 ', 9' of the two rotors, ie the sum of the "numbers of teeth" is thus 14.
- FIG. 3 shows the profile sections 7, 9 of the two rotors in the axial-perpendicular section.
- the main runner profile 7 has six helical ribs 7 'separated by grooves 7''The top surfaces of the ribs 7' lie on the outer enveloping circle Ka of the diameter Da profile The bottom surfaces of the grooves 7 '' lie on top Inner circle Ki with the diameter Di.
- the radial distance between the circles Ka and Ki is referred to as rib height or tooth height H. This is not greater, preferably less than 0.15 times the diameter Da of the outer circle Ka.
- the gas to be compressed in particular air supplied, which is preferably pre-compressed by one or more upstream compressor stages (not shown) already at an intermediate pressure, for example to a pressure in the range of 10th up to 15 bar, preferably 12 bar.
- This precompressed gas is through the profile sections 7, 9 of the two rotors 3, 5 in FIG. 1 conveyed to the right to a (not shown) outlet and thereby compressed to a final pressure, which is preferably in the range of 30 to 50 bar, in particular at about 40 bar.
- the rotors of the screw compressor are designed to be highly insensitive to the transverse axial forces generated by the compressed gas at these high pressures.
Description
- Die Erfindung betrifft einen Schraubenkompressor mit zwei in einem Rotorgehäuse achsparallel drehbar gelagerten Schraubenrotoren, von denen jeder einen Profilabschnitt mit schraubenförmig verlaufenden Rippen und Nuten aufweist. Die Rotoren greifen mit ihren Rippen und Nuten kämmend und abdichtend ineinander, und in Betrieb werden zwischen ihnen und dem Rotorgehäuse eingeschlossene Gasvolumina gefördert und verdichtet. Ein solcher schraubenkompressor ist aus der
US3986801 bekannt, die als nächstliegender Stand der Technik angesehen wird. - Bei der Gestaltung der Profile derartiger Schraubenrotoren ging das Bestreben bisher dahin, bei gegebenem Außendurchmesser der Rotorprofile möglichst große Volumina für das zwischen den Rotoren und dem Rotorgehäuse eingeschlossene, zu verdichtende Gasvolumen bereitzustellen, d. h. eine möglichst große volumetrische Ausnutzung des Rotorprofiles zu erzielen.
- Im Gegensatz dazu zielt die vorliegende Erfindung darauf ab, einen Schraubenkompressor zur Verfügung zu stellen, der sich für die Verdichtung von Gas auf sehr hohe Drücke, typischerweise im Bereich von 30 bis 50 bar, eignet und der insbesondere als letzte Stufe eines mehrstufigen, insbesondere dreistufigen Kompressoraggregats betrieben werden kann. Bei derart hohen Drücken sind die Rotoren durch das zwischen ihnen und dem Gehäuse unter hohem Druck eingeschlossene Gasvolumen starken queraxialen Kräften ausgesetzt, die im Sinne einer Durchbiegung der Rotoren wirken. Dies kann zu einer Beeinträchtigung der Abdichtung zwischen den Rotoren und damit zu einem Verlust an Wirkungsgrad führen. Auch kann wegen der Durchbiegung der Rotoren der radiale Spalt zwischen den Rotoren und dem Rotorgehäuse nicht so klein bemessen werden, wie dies zur Erzielung einer guten Abdichtung und eines hohen Wirkungsgrades wünschenswert wäre.
- Aufgabe der Erfindung ist es daher, einen Schraubenkompressor anzugeben, der sich vor allem für den Betrieb bei hohen Verdichtungsdrücken eignet.
- Die erfindungsgemäße Lösung der Aufgabe ist im Anspruch 1 angegeben. Der Unteranspruch bezieht sich auf eine vorteilhafte weitere Ausgestaltung der Erfindung.
- Es wurde gefunden, dass die in den Ansprüchen angegebene Gestaltung der Rotoren zu einem besonders günstigen Verhältnis zwischen einerseits der Biegesteifigkeit der Rotoren und andererseits der Größe des in den Schraubennuten der Rotoren eingeschlossenen komprimierten Gasvolumens, das die Biegekräfte verursacht, führt.
- Eine Ausführungsform der Erfindung wird im Folgenden anhand der Zeichnungen näher erläutert. Es zeigt
- Figur 1
- eine teilweise geschnittene Ansicht eines erfindungsgemäßen Schrauben- kompressors.
- Figur 2
- eine perspektivische Darstellung der Rotoren des Schraubenkompressors gemäß
Figur 1 . - Figur 3
- das Rotorprofil der beiden Rotoren im achssenkrechten Querschnitt.
- Der in
Figur 1 als Ausführungsbeispiel gezeigte Schraubenkompressor hat ein im Schnitt dargestelltes Rotorgehäuse 1, in welchem zwei Rotoren 3 und 5 parallelachsig drehbar gelagert sind. Die Drehachsen der Rotoren 3, 5 liegen in einer gemeinsamen vertikalen Ebene, die auch die Schnittebene für die Darstellung des Rotorgehäuses 1 ist. Jeder Rotor hat einen Profilabschnitt 7 bzw. 9, der ein Profil mit schraubenförmig verlaufenden Rippen bzw. Nuten aufweist, wobei die Rippen und Nuten der beiden Profilabschnitte 7, 9 kämmend ineinander greifen. An die Profilabschnitte 7, 9 schließen sich Wellenzapfen 7a, 7b, 9a, 9b an, mit deren Umfangsfläche Dichtungsringe 11 zusammenwirken, um den Rotor im Rotorgehäuse 1 abzudichten. Die Wellenzapfen 7a, 7b, 9a, 9b sind ferner durch Lager 13, 15 in dem Rotorgehäuse 1 drehbar gelagert. - Der in
Figur 1 obere Rotor 3 ist der Hauptläufer und weist an seinem inFigur 1 linken Ende eine Verlängerung 7c seines Wellenzapfens auf, die zur Aufnahme eines Antriebszahnrades (nicht dargestellt) bestimmt ist, das mit einem entsprechenden Zahnrad eines Antriebsgetriebes (nicht dargestellt) kämmt, um den Rotor 3 zur Drehung anzutreiben. An dem inFigur 1 rechten Ende weisen die beiden Rotoren 3, 5 zwei miteinander kämmende Zahnräder 17, 19 auf, die ein Synchronisiergetriebe bilden, das die Drehung von dem oberen Rotor 3 auf den unteren Rotor 5, der der Nebenläufer ist, im gewünschten Drehzahlverhältnis überträgt und dafür sorgt, dass die Profilabschnitte 7, 9 der Rotoren berührungsfrei ineinandergreifen. - Der beschriebene Schraubenkompressor ist vorzugsweise trockenlaufend, das heißt dem Verdichterraum wird kein Öl für Schmierung, Kühlung oder Abdichtung zugeführt. Die Rotorprofile greifen berührungsfrei und trotzdem abdichtend ineinander. Dies ist für alle Anwendungen vorteilhaft, bei denen es auf völlige Ölfreiheit des verdichteten Gases ankommt. Öl wird nur außerhalb des Verdichterraums, d. h. außerhalb des durch die Dichtungen 11 abgedichteten Bereichs, z. B. zur Schmierung des (nicht dargestellten) Antriebsgetriebes, der Lager 13, 15 und des Gleichlaufgetriebes 17, 19 zugeführt.
- In
Figur 2 sind die beiden Rotoren 3, 5 des Schraubenkompressors vonFigur 1 gesondert perspektivisch dargestellt. Man erkennt ausFigur 2 , dass der Rotor 3, der der Hauptläufer ist, einen Profilabschnitt 7 aufweist, dessen Profil von sechs schraubenförmig verlaufenden Rippen 7' gebildet wird. Der untere Rotor 5, der der Nebenläufer ist, hat einen Profilabschnitt 9 mit einem Profil, das von acht schraubenförmig verlaufenden Rippen 9' gebildet wird. Die Summe der Anzahlen der schraubenförmigen Rippen 7', 9' der beiden Rotoren, d. h. die Summe der "Zähnezahlen", beträgt somit 14. - Ferner sind in
Figur 2 die an den Profilabschnitt 7 bzw. 9 jedes der Rotoren 3, 5 beiderseits anschließenden Bereiche 7a, 7b, 9a, 9b der Wellenzapfen mit einem Durchmesser (D, D') dargestellt, der mehr als die Hälfte des Außendurchmessers des jeweiligen Profilabschnitts beträgt. -
Figur 3 zeigt die Profilabschnitte 7, 9 der beiden Rotoren im achssenkrechten Schnitt. Das Profil 7 des Hauptläufers weist sechs schraubenförmige Rippen 7' auf, die durch Nuten 7" voneinander getrennt sind. Die Kopfflächen der Rippen 7' liegen auf dem äußeren Hüllkreis Ka des Profils mit dem Durchmesser Da. Die Bodenflächen der Nuten 7" liegen auf dem Innenkreis Ki mit dem Durchmesser Di. Der radiale Abstand zwischen den Kreisen Ka und Ki wird als Rippenhöhe oder Zahnhöhe H bezeichnet. Diese ist nicht größer, vorzugsweise kleiner als das 0,15-fache des Durchmessers Da des Außenkreises Ka. Dasselbe gilt für die acht Rippen 9' und die sie trennenden Nuten 9" des unteren Rotors (Nebenläufers) 9, d. h. auch hier ist die Zahnhöhe H nicht größer als das 0,15-fache des Profilaußendurchmessers Da. - Bei Betrieb des in
Figur 1 gezeigten Schraubenkompressors wird seinem Ansaugraum 10, der angrenzend an das inFigur 1 linke Ende der Profilabschnitte 7, 9 in dem Rotorgehäuse 1 ausgebildet ist, das zu verdichtende Gas, insbesondere Luft zugeführt, das vorzugsweise von einer oder mehreren vorgeschalteten Kompressorstufen (nicht dargestellt) bereits auf einem Zwischendruck vorverdichtet ist, beispielsweise auf einen Druck im Bereich von 10 bis 15 bar, vorzugsweise 12 bar. Dieses vorverdichtete Gas wird durch die Profilabschnitte 7, 9 der beiden Rotoren 3, 5 inFigur 1 nach rechts zu einem (nicht dargestellten) Auslass gefördert und dabei auf einen Enddruck verdichtet, der vorzugsweise im Bereich von 30 bis 50 bar, insbesondere bei ca. 40 bar liegt. Die Rotoren des Schraubenkompressors sind so gestaltet, dass sie in hohem Maße unempfindlich gegen die vom komprimierten Gas bei diesen hohen Drücken erzeugten queraxialen Kräfte sind.
Claims (2)
- Schraubenkompressor mit zwei drehbar gelagerten, gegensinnig antreibbaren Rotoren (3, 5), die über einen Abschnitt ihrer Länge ein Profil (7, 9) mit schraubenförmigen Rippen (7', 9') und Nuten aufweisen und mit diesen Rippen und Nuten kämmend und abdichtend ineinandergreifen, wobei die Summe der Anzahlen der schraubenförmigen Rippen (7', 9') der beiden Rotoren mindestens 14 beträgt, und wobei jeder Rotor an den Profilabschnitt angrenzende Wellenzapfen (7a, 7b, 9a, 9b) aufweist, dadurch gekennzeichnet, dass die Rippenhöhe jedes Rotors (3, 5) nicht größer als das 0,15-fache des Profilaußendurchmessers (Da) des Rotors ist und dass der Durchmesser (D, D') jedes Wellenzapfens in dem an den Profilabschnitt (7, 9) angrenzenden Bereich nicht kleiner als die Hälfte des Profilaußendurchmessers (Da) ist.
- Schraubenkompressor nach Anspruch 1, wobei einer Rotoren der Hauptläufer (3) und der andere Rotor der Nebenläufer (5) ist, dadurch gekennzeichnet, dass das Profil (7) des Hauptläufers sechs Rippen (7') und das Profil (9) des Nebenläufers acht Rippen (9') aufweist.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102005058698 | 2005-12-08 | ||
PCT/EP2006/005556 WO2007065484A1 (de) | 2005-12-08 | 2006-06-09 | Schraubenkompressor |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1957798A1 EP1957798A1 (de) | 2008-08-20 |
EP1957798B1 true EP1957798B1 (de) | 2011-02-09 |
Family
ID=36763690
Family Applications (4)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP06754261.3A Active EP1979618B1 (de) | 2005-12-08 | 2006-06-09 | Mehrstufiges schraubenkompressoraggregat |
EP06754260.5A Active EP1957797B1 (de) | 2005-12-08 | 2006-06-09 | Schraubenkompressor mit kühlmantel |
EP06754262A Withdrawn EP1957799A1 (de) | 2005-12-08 | 2006-06-09 | Schraubenkompressor |
EP06762002A Active EP1957798B1 (de) | 2005-12-08 | 2006-06-09 | Schraubenkompressor |
Family Applications Before (3)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP06754261.3A Active EP1979618B1 (de) | 2005-12-08 | 2006-06-09 | Mehrstufiges schraubenkompressoraggregat |
EP06754260.5A Active EP1957797B1 (de) | 2005-12-08 | 2006-06-09 | Schraubenkompressor mit kühlmantel |
EP06754262A Withdrawn EP1957799A1 (de) | 2005-12-08 | 2006-06-09 | Schraubenkompressor |
Country Status (8)
Country | Link |
---|---|
US (4) | US7690901B2 (de) |
EP (4) | EP1979618B1 (de) |
CN (2) | CN101321954B (de) |
AT (1) | ATE498071T1 (de) |
DE (1) | DE502006008894D1 (de) |
ES (1) | ES2359015T3 (de) |
HK (1) | HK1127111A1 (de) |
WO (4) | WO2007065485A1 (de) |
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CN101498304B (zh) * | 2009-03-11 | 2011-06-15 | 宁波鲍斯能源装备股份有限公司 | 一种煤层气双螺杆压缩机组 |
DE102009019220B4 (de) * | 2009-04-30 | 2013-04-11 | Leistritz Pumpen Gmbh | Schraubenspindelpumpe |
US8339714B2 (en) | 2010-10-13 | 2012-12-25 | Olympus Imaging Corp. | Zoom lens and imaging apparatus incorporating the same |
JP5777379B2 (ja) * | 2011-04-05 | 2015-09-09 | 株式会社日立産機システム | 空気圧縮機 |
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US9828995B2 (en) | 2014-10-23 | 2017-11-28 | Ghh Rand Schraubenkompressoren Gmbh | Compressor and oil drain system |
DE102014019117B4 (de) * | 2014-12-19 | 2022-02-24 | Knorr-Bremse Systeme für Nutzfahrzeuge GmbH | Druckluftversorgungseinrichtung für Fahrzeug-Druckluftanlagen mit wenigstens einem Gehäuse aus Kunststoff |
US9803639B2 (en) * | 2014-12-19 | 2017-10-31 | Ghh-Rand Schraubenkompressoren Gmbh | Sectional sealing system for rotary screw compressor |
WO2016201173A1 (en) * | 2015-06-11 | 2016-12-15 | Eaton Corporation | Supercharger having constant lead helix angle timing gears |
CN105386972B (zh) * | 2015-12-09 | 2017-05-17 | 合肥工业大学 | 一种具有动密封结构的螺杆真空泵 |
US10718334B2 (en) | 2015-12-21 | 2020-07-21 | Ingersoll-Rand Industrial U.S., Inc. | Compressor with ribbed cooling jacket |
US10451061B2 (en) | 2016-05-06 | 2019-10-22 | Ingersoll-Rand Company | Compressor having non-contact and contact seals |
CN108071586A (zh) * | 2016-11-14 | 2018-05-25 | 上海汉钟精机股份有限公司 | 齿型转子组 |
TWI624596B (zh) * | 2017-03-15 | 2018-05-21 | 亞台富士精機股份有限公司 | 可被遠端監控的幫浦機台及幫浦監控系統 |
EP3382203A1 (de) | 2017-03-30 | 2018-10-03 | Roper Pump Company | Exzenterschneckenpumpe mit integriertem heizmantel |
CN108644117A (zh) * | 2018-07-25 | 2018-10-12 | 宁波鲍斯能源装备股份有限公司 | 一种三级螺杆传动结构及其螺杆压缩机 |
CN109139456A (zh) * | 2018-09-20 | 2019-01-04 | 宁波鲍斯能源装备股份有限公司 | 一种双级喷水螺杆主机 |
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US8342829B2 (en) * | 2005-12-08 | 2013-01-01 | Ghh Rand Schraubenkompressoren Gmbh | Three-stage screw compressor |
-
2006
- 2006-06-09 EP EP06754261.3A patent/EP1979618B1/de active Active
- 2006-06-09 WO PCT/EP2006/005557 patent/WO2007065485A1/de active Application Filing
- 2006-06-09 WO PCT/EP2006/005556 patent/WO2007065484A1/de active Application Filing
- 2006-06-09 US US12/094,363 patent/US7690901B2/en active Active
- 2006-06-09 ES ES06762002T patent/ES2359015T3/es active Active
- 2006-06-09 US US12/094,388 patent/US7713039B2/en active Active
- 2006-06-09 US US12/094,380 patent/US20080286129A1/en not_active Abandoned
- 2006-06-09 WO PCT/EP2006/005558 patent/WO2007065486A1/de active Application Filing
- 2006-06-09 AT AT06762002T patent/ATE498071T1/de active
- 2006-06-09 EP EP06754260.5A patent/EP1957797B1/de active Active
- 2006-06-09 CN CN200680045196XA patent/CN101321954B/zh not_active Expired - Fee Related
- 2006-06-09 WO PCT/EP2006/005559 patent/WO2007065487A1/de active Application Filing
- 2006-06-09 EP EP06754262A patent/EP1957799A1/de not_active Withdrawn
- 2006-06-09 CN CNA2006800452708A patent/CN101321955A/zh active Pending
- 2006-06-09 EP EP06762002A patent/EP1957798B1/de active Active
- 2006-06-09 DE DE502006008894T patent/DE502006008894D1/de active Active
-
2009
- 2009-06-03 HK HK09104996.7A patent/HK1127111A1/xx not_active IP Right Cessation
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Also Published As
Publication number | Publication date |
---|---|
CN101321954A (zh) | 2008-12-10 |
WO2007065487A1 (de) | 2007-06-14 |
US9091268B2 (en) | 2015-07-28 |
ATE498071T1 (de) | 2011-02-15 |
EP1957797B1 (de) | 2016-09-28 |
EP1957797A1 (de) | 2008-08-20 |
EP1957799A1 (de) | 2008-08-20 |
US20080286129A1 (en) | 2008-11-20 |
US7690901B2 (en) | 2010-04-06 |
EP1957798A1 (de) | 2008-08-20 |
WO2007065484A1 (de) | 2007-06-14 |
WO2007065485A1 (de) | 2007-06-14 |
DE502006008894D1 (de) | 2011-03-24 |
EP1979618A1 (de) | 2008-10-15 |
US20090004036A1 (en) | 2009-01-01 |
CN101321955A (zh) | 2008-12-10 |
ES2359015T3 (es) | 2011-05-17 |
US20080286138A1 (en) | 2008-11-20 |
EP1979618B1 (de) | 2016-04-27 |
US20130011285A1 (en) | 2013-01-10 |
WO2007065486A1 (de) | 2007-06-14 |
HK1127111A1 (en) | 2009-09-18 |
CN101321954B (zh) | 2012-06-13 |
US7713039B2 (en) | 2010-05-11 |
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