EP0959251A1 - Rotary gear compressor and method for its operation - Google Patents
Rotary gear compressor and method for its operation Download PDFInfo
- Publication number
- EP0959251A1 EP0959251A1 EP99109591A EP99109591A EP0959251A1 EP 0959251 A1 EP0959251 A1 EP 0959251A1 EP 99109591 A EP99109591 A EP 99109591A EP 99109591 A EP99109591 A EP 99109591A EP 0959251 A1 EP0959251 A1 EP 0959251A1
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- EP
- European Patent Office
- Prior art keywords
- neutral
- pressure
- space
- chamber
- delivery
- 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
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Classifications
-
- 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
- F04C27/00—Sealing arrangements in rotary-piston pumps specially adapted for elastic fluids
- F04C27/008—Sealing arrangements in rotary-piston pumps specially adapted for elastic fluids for other than working fluid, i.e. the sealing arrangements are not between working chambers of the machine
- F04C27/009—Shaft sealings specially adapted for pumps
Definitions
- the invention relates to a rotary tooth compressor with a a gear room, a neutral room and a funding room penetrating first pump shaft and one parallel second pump shaft, which from the gearbox through the neutral space and the funding area leads, the two pump shafts each in the delivery chamber have a rotor and wherein the delivery chamber to carry out the two pump shafts a labyrinth seal sealed off from the neutral room is.
- the invention further relates to a method for operating such a rotary tooth compressor.
- Such rotary tooth compressors are called dry running machines for the compression of gas by a pressure difference of 2 bar and are therefore known.
- Pressures as 3 bar (a) are suitable for rotary tooth compressors not because it will result in undesirable excessive wear the seals are coming.
- the well-known rotary tooth compressors have on both sides of the funding area a neutral space that is connected to the atmosphere.
- the invention is based on the problem of a rotary tooth compressor of the type mentioned at the beginning so that it has higher pressure differentials and higher absolute pressures than previously can compress without its seals subject to high wear. Furthermore should a method for operating such a rotary compressor be created.
- the first-mentioned problem is solved by that the gearbox and the neutral room are pressure-tight executed and each with a pressure medium connection are provided that the two pump shafts between the delivery room and the gear box and those from the Transmission shaft leading out to the pump shaft between the atmosphere and the gearbox a shaft seal are sealed, which one against the respective pump shaft adjacent to the delivery chamber has facing sealing lip.
- the speed compressor according to the invention enables it in one-step execution up to to 3 bar (a) and in two stages up to 5 up to 6 bar (a) to compress reliably. At the same time is ensured by the pressure-tight neutral space, that no process gas is leaked into the environment of the rotary compressor.
- the desired, reduced compared to the funding area Pressure in the neutral rooms is inevitable if the two neutral rooms each with the Have suction connection of the rotary tooth compressor.
- the second problem namely the creation of a Method for operating the rotary tooth compressor according to the invention, is solved according to the invention in that the gearbox-side, neutral room with an under the pressure in the delivery chamber and the gearbox with one under pressure in the production rooms, however pressure above atmospheric pressure becomes.
- the rotary tooth compressor according to the invention optimal with regard to the life of the shaft seals used.
- the gradual pressurization at the same time ensured that no gas from the neutral Space can get into the funding room.
- the rotary tooth compressor shown as a whole in FIG. 1 has in a housing 1 a delivery chamber 2, in which two rotors 3, 4 are arranged. Each of these rotors 3, 4 is arranged on a pump shaft 5, 6. To both The side of the delivery chamber 2 is a pressure-tight, neutral one Room 7, 8 provided, each with a pressure medium connection 9, 10 has. Seen in Figure 1 to the left of the neutral Room 7 is located in the housing 1, a gear room 11, which is also pressure-tight and one Has pressure medium connection 12. Located in gearbox 11 there is a gear 13, which the two pump shafts 5, 6 gears together. The pump shaft 6 leads out of the gear chamber 11 and is with a motor 14 flanged to the outside of the housing 1 connected.
- the pump shafts 5, 6 penetrate with their respective right end the right, neutral room 8 and are each stored in a pedestal storage room 15, 16, which is hermetically sealed from the outside.
- the pump shafts 5, 6 are between the delivery chamber 2 and the respective neutral room 8 each with a labyrinth seal 17, 18, 19, 20 sealed.
- Shaft seals 21, 22 seal the plummer block 15, 16 compared to the neutral Room 8 onwards.
- Corresponding shaft sealing rings 23, 24 seal the neutral space 7 with respect to the gear space 11 and a shaft seal 25 opposite the gear chamber 11 the atmosphere.
- a purge gas source 31 enables the gear chamber 11 and defined the two neutral rooms 7, 8 with a purge gas To apply pressure.
- This purge gas can the neutral spaces 7, 8 via an overflow valve 32 leave. This way you can go into the neutral Evacuate rooms 7, 8 penetrating process gas continuously.
- FIG. 1 This shows compared to FIG. 1 greatly increases the shaft seals located on the pump shaft 6 22, 24, 25. All three shaft seals 22, 24, 25 have one against the pump shaft 6 Sealing lip 26, 27, 28.
- the sealing lip 28 of the Shaft sealing ring 22 points away from the delivery chamber 2.
- Figure 2 also shows that the pillow block 16 has a pressure medium connection 30 and this Pressure medium connection 30 through a line 29 to the Pressure medium connection 10 of the right neutral room 8 connected is. The left one is also connected to this line 29 neutral room 7 connected. It is connected to the Suction side of the machine stage.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
- Sealing Using Fluids, Sealing Without Contact, And Removal Of Oil (AREA)
- Rotary Pumps (AREA)
- Supercharger (AREA)
Abstract
Description
Die Erfindung betrifft einen Drehzahnverdichter mit einer einen Getrieberaum, einen neutralen Raum und einen Förderraum durchdringenden ersten Pumpenwelle und einer hierzu parallelen zweiten Pumpenwelle, welche von dem Getrieberaum durch den neutralen Raum und den Förderraum führt, wobei die beiden Pumpenwellen jeweils in dem Förderraum einen Rotor aufweisen und wobei der Förderraum zur Durchführung der beiden Pumpenwellen jeweils durch eine Labyrinthabdichtung gegenüber dem neutralen Raum abgedichtet ist. Weiterhin betrifft die Erfindung ein Verfahren zum Betrieb eines solchen Drehzahnverdichters.The invention relates to a rotary tooth compressor with a a gear room, a neutral room and a funding room penetrating first pump shaft and one parallel second pump shaft, which from the gearbox through the neutral space and the funding area leads, the two pump shafts each in the delivery chamber have a rotor and wherein the delivery chamber to carry out the two pump shafts a labyrinth seal sealed off from the neutral room is. The invention further relates to a method for operating such a rotary tooth compressor.
Solche Drehzahnverdichter werden als trocken laufende Maschinen für die Verdichtung von Gas um eine Druckdifferenz von 2 bar eingesetzt und sind daher bekannt. Für höhere Drücke als 3 bar (a) eignen sich Drehzahnverdichter nicht, weil es dann zu einem unerwünscht starken Verschleiß der Dichtungen kommt. Die bekannten Drehzahnverdichter haben zu beiden Seiten des Förderraumes jeweils einen neutralen Raum, der Verbindung zur Atmosphäre hat.Such rotary tooth compressors are called dry running machines for the compression of gas by a pressure difference of 2 bar and are therefore known. For higher ones Pressures as 3 bar (a) are suitable for rotary tooth compressors not because it will result in undesirable excessive wear the seals are coming. The well-known rotary tooth compressors have on both sides of the funding area a neutral space that is connected to the atmosphere.
Für die Gasverdichtung, insbesondere von Sauerstoff, auf absolute Drücke von 5 bis 6 bar wurden bis jetzt ölfreie Kolbenverdichter verwendet, die sehr aufwendig aufgebaut und deshalb teuer sind. Weiterhin erfordern sie einen hohen Serviceaufwand, da etwa alle 6.000 bis 8.000 Betriebsstunden die Kolbenringe und Ventile ausgewechselt werden müssen. For gas compression, especially of oxygen absolute pressures of 5 to 6 bar have so far been oil-free Piston compressor used, which is very complex and are therefore expensive. Furthermore, they require a high one Service requirements, as every 6,000 to 8,000 operating hours the piston rings and valves replaced Need to become.
Der Erfindung liegt das Problem zugrunde, einen Drehzahnverdichter der eingangs genannten Art so umzugestalten, dass er auf höhere Druckdifferenzen und höhere Absolutdrücke als bisher verdichten kann, ohne dass seine Dichtungen einem hohen Verschleiß unterliegen. Weiterhin soll ein Verfahren zum Betrieb eines solchen Drehzahnverdichters geschaffen werden.The invention is based on the problem of a rotary tooth compressor of the type mentioned at the beginning so that it has higher pressure differentials and higher absolute pressures than previously can compress without its seals subject to high wear. Furthermore should a method for operating such a rotary compressor be created.
Das erstgenannte Problem wird erfindungsgemäß dadurch gelöst, dass der Getrieberaum und der neutrale Raum druckdicht ausgeführt und jeweils mit einem Druckmittelanschluss versehen sind, dass die beiden Pumpenwellen zwischen dem Förderraum und dem Getrieberaum und die aus dem Getrieberaum nach außen herausführende Pumpenwelle zwischen der Atmosphäre und dem Getrieberaum jeweils durch einen Wellendichtring abgedichtet sind, welcher eine gegen die jeweilige Pumpenwelle anliegende, zum Förderraum hin gerichtete Dichtlippe aufweist.According to the invention, the first-mentioned problem is solved by that the gearbox and the neutral room are pressure-tight executed and each with a pressure medium connection are provided that the two pump shafts between the delivery room and the gear box and those from the Transmission shaft leading out to the pump shaft between the atmosphere and the gearbox a shaft seal are sealed, which one against the respective pump shaft adjacent to the delivery chamber has facing sealing lip.
Bei einem solchen Drehzahlverdichter kann man den neutralen Raum und den Getrieberaum so abgestuft druckbeaufschlagen, dass die Wellendichtringe jeweils nur einem Teil der Druckdifferenz zwischen dem Druck im Förderraum und dem Atmosphärendruck ausgesetzt sind. Man kann zum Beispiel bei einem absoluten Druck im Förderraum von 5 bar, so dass ein mittlerer Druck in den Labyrinthabdichtungen von 4 bar ansteht, im neutralen Raum einen absoluten Druck von 3 bar und im Getrieberaum einen absoluten Druck von 2 bar einstellen. Die Wellendichtringe zwischen dem neutralen Raum und dem Getrieberaum und der Wellendichtring zwischen dem Getrieberaum und der Atmosphäre werden dann jeweils nur mit einer Druckdifferenz von 1 bar beansprucht, was zu einer langen Lebensdauer dieser Dichtungen führt. Der erfindungsgemäße Drehzahlverdichter ermöglicht es in einstufiger Ausführung bis auf 3 bar (a) und in zweistufiger Ausführung bis auf 5 bis 6 bar (a) betriebssicher zu komprimieren. Zugleich wird durch den druckdichten neutralen Raum sichergestellt, dass kein Prozessgas als Leckgas in die Umgebung des Drehzahnverdichters gelangen kann.With such a speed compressor you can use the neutral one Pressurize the space and the gearbox area so graduated that that the shaft seals only one Part of the pressure difference between the pressure in the delivery chamber and are exposed to atmospheric pressure. You can go to Example with an absolute pressure in the delivery chamber of 5 bar so that a medium pressure in the labyrinth seals of 4 bar, an absolute one in neutral space Pressure of 3 bar and an absolute one in the gearbox Set pressure of 2 bar. The shaft seals between the neutral space and the gearbox and the Shaft seal between the gearbox and the atmosphere are then only with a pressure difference stressed by 1 bar, resulting in a long service life of these seals leads. The speed compressor according to the invention enables it in one-step execution up to to 3 bar (a) and in two stages up to 5 up to 6 bar (a) to compress reliably. At the same time is ensured by the pressure-tight neutral space, that no process gas is leaked into the environment of the rotary compressor.
Bei einem Drehzahnverdichter, bei dem die beiden Pumpenwellen an der dem Getrieberaum gegenüberliegenden Seite des Förderraumes jeweils in einem Stehlagerraum gelagert sind, wobei zwischen dem Stehlagerraum und dem Förderraum ebenfalls ein neutraler Raum vorgesehen ist, kann man ebenfalls eine lange Lebensdauer des dort anzuordnenden Wellendichtringes erreichen, wenn gemäß einer Weiterbildung der Erfindung der Stehlagerraum und der zwischen ihm und dem Förderraum liegende neutrale Raum druckdicht ausgeführt und jeweils mit einem Druckmittelanschluss versehen sind und wenn jeder Stehlagerraum durch einen gegen die Pumpenwelle mit einer Dichtlippe anliegenden Wellendichtring abgedichtet ist.With a rotary tooth compressor in which the two pump shafts on the side opposite the gearbox of the delivery room each stored in a pedestal storage room are, between the pillow block and the delivery room a neutral room is also provided, one can also a long life of the to be arranged there Achieve shaft sealing ring if according to a training the invention of the pillow block and the space between it and the neutral space located in the delivery chamber is pressure-tight and each with a pressure medium connection and if each pillow block is countered by one the pump shaft with a shaft sealing ring in contact with a sealing lip is sealed.
Der gewünschte, gegenüber dem Förderraum verringerte Druck in den neutralen Räumen stellt sich zwangsläufig ein, wenn die beiden neutralen Räume jeweils mit der Saugseite des Drehzahnverdichters Verbindung haben.The desired, reduced compared to the funding area Pressure in the neutral rooms is inevitable if the two neutral rooms each with the Have suction connection of the rotary tooth compressor.
Das zweitgenannte Problem, nämlich die Schaffung eines Verfahrens zum Betrieb des erfindungsgemäßen Drehzahnverdichters, wird gemäß der Erfindung dadurch gelöst, dass der getrieberaumseitige, neutrale Raum mit einem unter dem Druck im Förderraum liegenden Druck und der Getrieberaum mit einem unter dem Druck in den Förderräumen jedoch über dem Atmosphärendruck liegenden Druck beaufschlagt wird.The second problem, namely the creation of a Method for operating the rotary tooth compressor according to the invention, is solved according to the invention in that the gearbox-side, neutral room with an under the pressure in the delivery chamber and the gearbox with one under pressure in the production rooms, however pressure above atmospheric pressure becomes.
Hierdurch wird der erfindungsgemäße Drehzahnverdichter bezüglich der Lebensdauer der Wellendichtringe optimal eingesetzt. Durch die abgestufte Druckbeaufschlagung wird zugleich sichergestellt, dass kein Gas aus dem neutralen Raum in den Förderraum gelangen kann.As a result, the rotary tooth compressor according to the invention optimal with regard to the life of the shaft seals used. The gradual pressurization at the same time ensured that no gas from the neutral Space can get into the funding room.
Ein Eindringen von Fett von den Stehlagern in den Förderraum lässt sich auf einfache Weise dadurch vermeiden, dass auch der stehlagerraumseitige, neutrale Raum mit einem unter dem Druck im Förderraum liegenden Druck beaufschlagt wird.Penetration of grease from the plummer block bearings into the pumping chamber can be easily avoided by that the neutral storage-room-side, neutral room with one pressurized under the pressure in the delivery chamber becomes.
Günstig ist es auch, wenn der Stehlagerraum und der ihn vom Förderraum trennende neutrale Raum an eine gemeinsame Druckmittelquelle angeschlossen sind. Hierdurch wird eine Belastung des Wellendichtringes des Stehlagers durch eine Druckdifferenz gänzlich ausgeschlossen. Auch beim Anfahren und Stillsetzen des Drehzahnverdichters können durch diese Druckmittelverbindung keine Druckdifferenzen auf den Wellendichtring des Stehlagers wirken.It is also favorable if the pedestal storage room and him neutral space separating from the funding area to a common one Pressure medium source are connected. This will create a Loading of the shaft sealing ring of the pillow block bearing by Pressure difference completely excluded. Even when starting off and the rotary compressor can be stopped this pressure medium connection has no pressure differences the shaft sealing ring of the pillow block.
Aus dem Förderraum in die neutralen Räume einsickerndes Prozessgas kann aus den neutralen Räumen kontinuierlich entfernt werden, wenn gemäß einer anderen Weiterbildung der Erfindung die neutralen Räume zur Druckbeaufschlagung mit einer Spülgasquelle verbunden sind und jeweils einen durch ein Überströmventil geregelten Spülgasauslass aufweisen. Ein solcher kontinuierlicher Spülgasstrom führt zugleich zu einer Temperaturabsenkung an den Wellendichtringen und dadurch zu einer Erhöhung ihrer Standzeit. Außerdem werden Getriebeölansammlungen im neutralen Raum bei Undichtigkeit am Wellendichtring vermieden.Something that seeps into the neutral rooms from the production area Process gas can flow continuously from the neutral rooms be removed if according to another training the invention, the neutral pressurized spaces are connected to a purge gas source and one each have a purge gas outlet regulated by an overflow valve. Such a continuous purge gas flow leads at the same time to a temperature reduction on the shaft sealing rings and thereby an increase in their service life. Furthermore become gear oil accumulations in neutral space avoided in the event of a leak on the shaft sealing ring.
Die Erfindung lässt verschiedene Ausführungsformen zu. Zur weiteren Verdeutlichung ihres Grundprinzips sind zwei davon in der Zeichnung dargestellt und werden nachfolgend beschrieben. Diese zeigt in
- Fig.1
- einen Längsschnitt durch einen Drehzahnverdichter nach der Erfindung,
- Fig.2
- eine Prinzipskizze, welche im Schnitt die
Anordnung und Gestaltung der Wellendichtringe
des Drehzahnverdichters und ihre Druckmittelversorgung
sowie eine gegenüber
Figur 1 geänderte Gasbeaufschlagung zeigt.
- Fig. 1
- 2 shows a longitudinal section through a rotary tooth compressor according to the invention,
- Fig. 2
- a schematic diagram, which shows in section the arrangement and design of the shaft sealing rings of the rotary compressor and their pressure medium supply as well as a changed gas supply compared to Figure 1.
Der in Figur 1 als Ganzes dargestellte Drehzahnverdichter
hat in einem Gehäuse 1 einen Förderraum 2, in welchem
zwei Rotoren 3, 4 angeordnet sind. Jeder dieser Rotoren
3, 4 ist auf einer Pumpenwelle 5, 6 angeordnet. Zu beiden
Seiten des Förderraumes 2 ist ein druckdichter, neutraler
Raum 7, 8 vorgesehen, der jeweils einen Druckmittelanschluss
9, 10 hat. In Figur 1 gesehen links von dem neutralen
Raum 7 befindet sich im Gehäuse 1 ein Getrieberaum
11, der ebenfalls druckdicht ausgeführt ist und einen
Druckmittelanschluss 12 aufweist. Im Getrieberaum 11 befindet
sich ein Getriebe 13, welches die beiden Pumpenwellen
5, 6 getrieblich miteinander verbindet. Die Pumpenwelle
6 führt aus dem Getrieberaum 11 heraus und ist
mit einem außen an dem Gehäuse 1 angeflanschten Motor 14
verbunden.The rotary tooth compressor shown as a whole in FIG. 1
has in a housing 1 a
Die Pumpenwellen 5, 6 durchdringen mit ihrem jeweils
rechten Ende den rechten, neutralen Raum 8 und sind jeweils
in einem Stehlagerraum 15, 16 gelagert, welcher
nach außen hin hermetisch verschlossen ist. Die Pumpenwellen
5, 6 sind zwischen dem Förderraum 2 und dem jeweiligen
neutralen Raum 8 jeweils durch eine Labyrinthabdichtung
17, 18, 19, 20 abgedichtet. Wellendichtringe 21,
22 dichten die Stehlagerräume 15, 16 gegenüber dem neutralen
Raum 8 ab. Entsprechende Wellendichtringe 23, 24
dichten den neutralen Raum 7 gegenüber dem Getrieberaum
11 und ein Wellendichtring 25 den Getrieberaum 11 gegenüber
der Atmosphäre ab. The
Eine Spülgasquelle 31 ermöglicht es, den Getrieberaum 11
und die beiden neutralen Räume 7, 8 mit einem Spülgas definierten
Druck zu beaufschlagen. Dieses Spülgas vermag
über ein Überströmventil 32 die neutralen Räume 7, 8 zu
verlassen. Auf diese Weise kann man in die neutralen
Räume 7, 8 eindringendes Prozessgas kontinuierlich abführen.A
Zur weiteren Erläuterung der Erfindung wird nunmehr auf
die Figur 2 Bezug genommen. Diese zeigt gegenüber Figur 1
stark vergrößert die auf der Pumpenwelle 6 sitzenden Wellendichtringe
22, 24, 25. Alle drei Wellendichtringe 22,
24, 25 haben eine gegen die Pumpenwelle 6 anliegende
Dichtlippe 26, 27, 28. Die Dichtlippen 26, 27 der Wellendichtringe
24, 25, welche den Getrieberaum 11 zur Atmosphäre
und zu dem neutralen Raum 7 hin abdichten, weisen
in Richtung des Förderraumes 2. Die Dichtlippe 28 des
Wellendichtringes 22 weist vom Förderraum 2 weg.To further explain the invention, reference is now made to
the figure 2 referred. This shows compared to FIG. 1
greatly increases the shaft seals located on the
Die Figur 2 lässt weiterhin erkennen, dass der Stehlagerraum
16 einen Druckmittelanschluss 30 hat und dieser
Druckmittelanschluss 30 durch eine Leitung 29 mit dem
Druckmittelanschluss 10 des rechten neutralen Raumes 8
verbunden ist. An diese Leitung 29 ist auch der linke
neutrale Raum 7 angeschlossen. Sie hat Verbindung mit der
Saugseite der Maschinenstufe.Figure 2 also shows that the
Nicht dargestellt ist eine Ausführungsform, bei der die
Pumpenwellen 5, 6 die Stehlagerräume 15, 16 durchdringen
und dann mit entsprechenden Pumpenwellen eines zweiten
Drehzahnverdichters verbunden sind. Bei einer solchen
Ausführungsform empfiehlt sich wiederum die zuvor für den
Getrieberaum und den neutralen Raum beschriebene, abgestufte
Druckbeaufschlagung. An embodiment is not shown in which the
Pump shafts 5, 6 penetrate the
- 11
- Gehäusecasing
- 22nd
- FörderraumFunding area
- 33rd
- Rotorrotor
- 44th
- Rotorrotor
- 55
- PumpenwellePump shaft
- 66
- PumpenwellePump shaft
- 77
- neutraler Raumneutral space
- 88th
- neutraler Raumneutral space
- 99
- DruckmittelanschlussPressure medium connection
- 1010th
- DruckmittelanschlussPressure medium connection
- 1111
- GetrieberaumGearbox
- 1212th
- DruckmittelanschlussPressure medium connection
- 1313
- Getriebetransmission
- 1414
- Motorengine
- 1515
- StehlagerraumPedestal storage room
- 1616
- StehlagerraumPedestal storage room
- 1717th
- LabyrinthabdichtungLabyrinth seal
- 1818th
- LabyrinthabdichtungLabyrinth seal
- 1919th
- LabyrinthabdichtungLabyrinth seal
- 2020th
- Labyrinthabdichtung Labyrinth seal
- 2121
- WellendichtringShaft seal
- 2222
- WellendichtringShaft seal
- 2323
- WellendichtringShaft seal
- 2424th
- WellendichtringShaft seal
- 2525th
- WellendichtringShaft seal
- 2626
- DichtlippeSealing lip
- 2727
- DichtlippeSealing lip
- 2828
- DichtlippeSealing lip
- 2929
- Leitungmanagement
- 3030th
- DruckmittelanschlussPressure medium connection
- 3131
- SpülgasquellePurge gas source
- 3232
- ÜberströmventilOverflow valve
Claims (7)
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE19822283A DE19822283A1 (en) | 1998-05-18 | 1998-05-18 | Rotary tooth compressor and method for operating one |
DE19822283 | 1998-05-18 |
Publications (2)
Publication Number | Publication Date |
---|---|
EP0959251A1 true EP0959251A1 (en) | 1999-11-24 |
EP0959251B1 EP0959251B1 (en) | 2004-05-19 |
Family
ID=7868186
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP99109591A Expired - Lifetime EP0959251B1 (en) | 1998-05-18 | 1999-05-14 | Rotary gear compressor and method for its operation |
Country Status (3)
Country | Link |
---|---|
EP (1) | EP0959251B1 (en) |
AT (1) | ATE267346T1 (en) |
DE (2) | DE19822283A1 (en) |
Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP1236902A2 (en) * | 2001-02-28 | 2002-09-04 | Kabushiki Kaisha Toyota Jidoshokki | Shaft seal structure of vacuum pumps |
WO2007065487A1 (en) * | 2005-12-08 | 2007-06-14 | Ghh Rand Schraubenkompressoren Gmbh | Helical screw compressor |
CN100400881C (en) * | 2002-08-23 | 2008-07-09 | 株式会社丰田自动织机 | Axle sealing structure for vacuum pump |
ITVI20130021A1 (en) * | 2013-01-31 | 2013-05-02 | Virgilio Mietto | VOLUMETRIC COMPRESSOR EQUIPPED WITH A IMPROVED LUBRICATION SYSTEM. |
EP3341602A4 (en) * | 2015-08-25 | 2019-06-19 | Eaton Intelligent Power Limited | High pressure rotor seal configuration for supercharger |
Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB559226A (en) * | 1942-08-07 | 1944-02-09 | Douglas Rudolf Pobjoy | Improvements in and relating to rotary pumps |
GB2116634A (en) * | 1982-03-10 | 1983-09-28 | Fiat Auto Spa | Rotary positive-displacement fluid-machines |
JPH05296171A (en) * | 1992-04-13 | 1993-11-09 | Ulvac Japan Ltd | Shaft seal mechanism for positive displacement vacuum pump without using sealing fluid |
EP0775812A1 (en) * | 1995-11-22 | 1997-05-28 | Ishikawajima-Harima Heavy Industries Co., Ltd. | Seal arrangement for engine-driven supercharger |
Family Cites Families (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4755115A (en) * | 1984-11-21 | 1988-07-05 | Atsugi Motor Parts Company, Limited | Shaft seal assembly for compressor |
DE4301293C2 (en) * | 1993-01-15 | 1996-07-11 | Mannesmann Ag | Device for removing small amounts of lubricant and coolant leaks |
DE29506010U1 (en) * | 1995-04-07 | 1996-08-08 | Armatec FTS-Armaturen GmbH & Co KG, 88239 Wangen | Rotary lobe pump |
DE19626515A1 (en) * | 1996-07-02 | 1998-01-08 | Ghh Borsig Turbomaschinen Gmbh | Sealing rings for screw compressor |
DE19633651A1 (en) * | 1996-08-21 | 1998-02-26 | Leybold Vakuum Gmbh | Dry vacuum machine with shaft passage |
-
1998
- 1998-05-18 DE DE19822283A patent/DE19822283A1/en not_active Withdrawn
-
1999
- 1999-05-14 DE DE59909504T patent/DE59909504D1/en not_active Expired - Fee Related
- 1999-05-14 EP EP99109591A patent/EP0959251B1/en not_active Expired - Lifetime
- 1999-05-14 AT AT99109591T patent/ATE267346T1/en not_active IP Right Cessation
Patent Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB559226A (en) * | 1942-08-07 | 1944-02-09 | Douglas Rudolf Pobjoy | Improvements in and relating to rotary pumps |
GB2116634A (en) * | 1982-03-10 | 1983-09-28 | Fiat Auto Spa | Rotary positive-displacement fluid-machines |
JPH05296171A (en) * | 1992-04-13 | 1993-11-09 | Ulvac Japan Ltd | Shaft seal mechanism for positive displacement vacuum pump without using sealing fluid |
EP0775812A1 (en) * | 1995-11-22 | 1997-05-28 | Ishikawajima-Harima Heavy Industries Co., Ltd. | Seal arrangement for engine-driven supercharger |
Non-Patent Citations (1)
Title |
---|
PATENT ABSTRACTS OF JAPAN vol. 18, no. 90 (M - 1560) 15 February 1994 (1994-02-15) * |
Cited By (8)
Publication number | Priority date | Publication date | Assignee | Title |
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EP1236902A2 (en) * | 2001-02-28 | 2002-09-04 | Kabushiki Kaisha Toyota Jidoshokki | Shaft seal structure of vacuum pumps |
EP1236902A3 (en) * | 2001-02-28 | 2004-04-14 | Kabushiki Kaisha Toyota Jidoshokki | Shaft seal structure of vacuum pumps |
CN100400881C (en) * | 2002-08-23 | 2008-07-09 | 株式会社丰田自动织机 | Axle sealing structure for vacuum pump |
WO2007065487A1 (en) * | 2005-12-08 | 2007-06-14 | Ghh Rand Schraubenkompressoren Gmbh | Helical screw compressor |
US7713039B2 (en) | 2005-12-08 | 2010-05-11 | Gmbh Rand Schraubenkowpressoren Gmbh | Helical screw compressor having a vented sealing arrangement |
US9091268B2 (en) | 2005-12-08 | 2015-07-28 | Ghh Rand Schraubenkompressoren Gmbh | Three-stage screw compressor |
ITVI20130021A1 (en) * | 2013-01-31 | 2013-05-02 | Virgilio Mietto | VOLUMETRIC COMPRESSOR EQUIPPED WITH A IMPROVED LUBRICATION SYSTEM. |
EP3341602A4 (en) * | 2015-08-25 | 2019-06-19 | Eaton Intelligent Power Limited | High pressure rotor seal configuration for supercharger |
Also Published As
Publication number | Publication date |
---|---|
DE19822283A1 (en) | 1999-11-25 |
ATE267346T1 (en) | 2004-06-15 |
DE59909504D1 (en) | 2004-06-24 |
EP0959251B1 (en) | 2004-05-19 |
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