EP1070848A1 - Positive displacement machine for compressible fluids - Google Patents

Positive displacement machine for compressible fluids Download PDF

Info

Publication number
EP1070848A1
EP1070848A1 EP99114031A EP99114031A EP1070848A1 EP 1070848 A1 EP1070848 A1 EP 1070848A1 EP 99114031 A EP99114031 A EP 99114031A EP 99114031 A EP99114031 A EP 99114031A EP 1070848 A1 EP1070848 A1 EP 1070848A1
Authority
EP
European Patent Office
Prior art keywords
slope
displacement machine
motors
machine according
inlet
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
Application number
EP99114031A
Other languages
German (de)
French (fr)
Other versions
EP1070848B1 (en
Inventor
Heiner Dr. Kösters
Guido Dr. Keller
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Sterling Fluid Systems Germany GmbH
Original Assignee
Sterling Fluid Systems Germany GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Sterling Fluid Systems Germany GmbH filed Critical Sterling Fluid Systems Germany GmbH
Priority to DK99114031T priority Critical patent/DK1070848T3/en
Priority to AT99114031T priority patent/ATE264457T1/en
Priority to DE59909182T priority patent/DE59909182D1/en
Priority to ES99114031T priority patent/ES2219956T3/en
Priority to EP99114031A priority patent/EP1070848B1/en
Priority to NO20003590A priority patent/NO323484B1/en
Priority to ZA200003568A priority patent/ZA200003568B/en
Priority to KR1020000041054A priority patent/KR100573752B1/en
Priority to JP2000217626A priority patent/JP2001055992A/en
Priority to SG200003980A priority patent/SG86422A1/en
Priority to CA002314124A priority patent/CA2314124C/en
Priority to AU48703/00A priority patent/AU775135B2/en
Priority to US09/619,600 priority patent/US6359411B1/en
Publication of EP1070848A1 publication Critical patent/EP1070848A1/en
Application granted granted Critical
Publication of EP1070848B1 publication Critical patent/EP1070848B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B29/00—Other pumps with movable, e.g. rotatable cylinders
    • 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
    • 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
    • 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
    • F04C2240/00—Components
    • F04C2240/40—Electric motor
    • F04C2240/402—Plurality of electronically synchronised motors
    • 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
    • F04C2240/00—Components
    • F04C2240/50—Bearings
    • F04C2240/51—Bearings for cantilever assemblies

Definitions

  • the invention relates to a displacement machine for compressible Media, especially dry-running vacuum pump, with at least two shafts with rotors acting as helical Profile bodies are formed and their profiles during rotation mesh like a gear and run without contact to each other, the slope of the helical profile body decreases from inlet to outlet.
  • the object of the invention is to provide a displacement machine of the type mentioned, which is a cheaper Shows pumping behavior and increases the delivery rate is.
  • the solution according to the invention is that the helical Profile body are double and the Slopes at the inlet end and outlet end of the helical Profile bodies are constant and in between of the larger Slope at the inlet end to the smaller slope at the outlet end the slope decreases continuously.
  • the slope is therefore constant at the inlet end. That’s why original delivery volume the size of the slope on Inlet end corresponds. This funding volume will not reduced that the slope decreases immediately.
  • a constant slope is again provided at the outlet end, which is less than the slope at the inlet end. This will the mentioned problems of backflow are greatly reduced, because over one turn or even several turns in the there is essentially constant pressure. This also makes the Final pressure of the pump reduced. At the same time because of the smaller funding volume reduces the power consumption.
  • the slopes are at the inlet and outlet ends constant over at least one turn.
  • the slope at the outlet end is constant over at least two turns. This gives you not only get better sealing and less backflow, but also better dissipation of the heat of compression. This then arises with a dry-running vacuum pump the heat of compression through the volume reduction and Heat of compression due to the penetration of outside air at the outlet end no longer in the same place and can therefore do better be dissipated.
  • the number of turns over which the slope is constant depends on the desired operating conditions of the pump.
  • a particularly favorable behavior of the displacement machine in particular in the vacuum range is obtained if provided is that the shafts are each driven by their own electric motors be, the angular positions of the shafts with resolvers the motors are determined on the basis of their signals be electronically synchronized, and being the waves Have gears that mesh and their angular play is smaller than that of the profile body.
  • the rotors are not driven by gears, but are completely contact-free thanks to our own electric motors driven, the gears only have the purpose prevent in the event of failure of the electronic synchronization, that the sensitive surfaces of the rotors touch and get damaged. Instead, the Touch gears, which is not a problem, in particular, if they are provided with the appropriate surface.
  • Three-phase motors have proven to be particularly suitable for operation proven with permanent magnetic rotor as drive.
  • Fig. 1 there are one of several Parts of assembled pump housing 1 with bearings 2 two shafts 3 stored on which profile body 4 are attached, which interlock and in the pump chamber 5 through a connection 13 that Suck the medium to be pumped from above and not through the bottom Eject the openings shown.
  • the waves 3 and the profile body 4 are driven by electric motors 6, whereby for each shaft 3 a separate electric motor 6 is provided.
  • the motors 6 are made using resolvers 8 electronically synchronized. In adverse operating conditions, if the electronic synchronization is not sufficient, first touch the gears 7 because they are one have less angular play than the rotors 4. Usually but do not touch the gears 7, so that lubrication of these gears can be dispensed with.
  • rotors according to the invention are shown, in which the slope decreases from the top (inlet end) to the bottom (outlet end).
  • the slope S 1 has a constant value over at least one turn.
  • the range of constant slope S 3 advantageously extends over at least two turns of the rotors 4.
  • the slope S 2 changes continuously from the value of S 1 to the value of S 3 .

Abstract

The displacement machine has at least two shafts with rotors in the form of spiral strip bodies (4) engaging with each other during rotation. The strip bodies are in two-start form. The rises (S1, S3) at the inlet ends and outlet ends of the strip bodies are constant, but between them, the rise (S2) decreases from the greater rise (S1) at the inlet end to the lesser rise (S3) at the outlet end.

Description

Die Erfindung betrifft eine Verdrängermaschine für kompressible Medien, insbesondere trockenlaufende Vakuumpumpe, mit mindestens zwei Wellen mit Rotoren, die als schraubenförmige Profilkörper ausgebildet sind und deren Profile bei der Drehung zahnradartig ineinandergreifen und berührungsfrei zueinanderlaufen, wobei die Steigung der schraubenförmigen Profilkörper vom Einlaß zum Auslaß abnimmt.The invention relates to a displacement machine for compressible Media, especially dry-running vacuum pump, with at least two shafts with rotors acting as helical Profile bodies are formed and their profiles during rotation mesh like a gear and run without contact to each other, the slope of the helical profile body decreases from inlet to outlet.

Bei einer bekannten Verdrängermaschine dieser Art (DE 195 30 662 A) werden zwei ineinandergreifende Profilkörper verwendet. Durch diese wird am Einlaßende ein bestimmtes Volumen eingeschlossen, das sich dann bei Drehung der Rotoren zum Auslaßende bewegt. Dabei findet, da die Steigung abnimmt und damit das eingeschlossene Fördervolumen zum Auslaßende hin kleiner wird, eine Kompression statt. Auf diese Weise wird das kompressible Medium vom Einlaßende zum Auslaßende gefördert und dabei komprimiert. Die kontinuierlich sich ändernde Steigung bewirkt zwar die Komprimierung, hat aber folgende Nachteile. In a known displacement machine of this type (DE 195 30 662 A) two interlocking profile bodies are used. This creates a certain volume at the inlet end included, which then turns when the rotors rotate Outlet end moved. It takes place as the slope decreases and thus the included delivery volume towards the outlet end becomes smaller, a compression takes place. That way the compressible medium is conveyed from the inlet end to the outlet end and compressed. The continuously changing Slope does the compression, but it has the following Disadvantage.

Da am Einlaßende die Steigung sich sofort verringert, ist das Fördervolumen kleiner, als es der Steigung direkt am Einlaßende entsprechen würde. Dies führt zu einer Begrenzung des Saugvermögens. Auf der Auslaßseite findet wegen der abnehmenden Steigung und Verringerung des Fördervolumens bis zum Ende der Rotoren dauernd noch Komprimierung statt, so daß Druckdifferenzen zwischen dem momentan letzten noch nicht geöffneten Fördervolumen und dem folgenden Fördervolumen existieren, die über nicht zu vermeidende Spalten zwischen den Rotoren und den Wänden zu Rückströmung des Mediums in das von der Einlaßseite her folgende Fördervolumen oder die folgenden Fördervolumen Anlaß geben, wodurch ebenfalls die Förderleistung verringert wird. Für die Leistungsaufnahme ist das Volumen der Förderkammer im Moment des Öffnens am Auslaßende maßgeblich. Da dieses wegen der stetig sich verringernden Steigung noch nicht den Wert angenommen, der der Steigung am Auslaßende entspricht, ergibt sich ein beträchtlicher Leistungsverlust.Since the slope decreases immediately at the inlet end, that is Delivery volume less than the slope directly at the inlet end would correspond. This leads to a limitation of the Pumping speed. On the outlet side takes place because of the decreasing Increase and decrease of the funding volume to the end the rotors are still under compression, so that pressure differences between the last one not currently open Funding volume and the following funding volume exist, the unavoidable gaps between the rotors and the walls to backflow the medium into that of the The following delivery volume or the following on the inlet side Funding volume give cause, which also the funding capacity is reduced. Volume is for power consumption the delivery chamber at the moment of opening at the outlet end essential. Because this is due to the steadily decreasing Slope has not yet assumed the value that corresponds to the slope on Corresponds to the outlet end, there is a considerable loss of performance.

Die Aufgabe der Erfindung besteht in der Schaffung einer Verdrängermaschine der eingangs genannten Art, die ein günstigeres Pumpverhalten zeigt und bei der die Förderleistung erhöht ist.The object of the invention is to provide a displacement machine of the type mentioned, which is a cheaper Shows pumping behavior and increases the delivery rate is.

Die erfindungsgemäße Lösung besteht darin, daß die schraubenförmigen Profilkörper zweigängig ausgebildet sind und die Steigungen am Einlaßende und Auslaßende der schraubenförmigen Profilkörper konstant sind und dazwischen von der größeren Steigung am Einlaßende zur kleineren Steigung am Auslaßende die Steigung kontinuierlich abnimmt. The solution according to the invention is that the helical Profile body are double and the Slopes at the inlet end and outlet end of the helical Profile bodies are constant and in between of the larger Slope at the inlet end to the smaller slope at the outlet end the slope decreases continuously.

Die Steigung ist also am Einlaßende konstant. Dadurch hat das ursprüngliche Fördervolumen die Größe, die der Steigung am Einlaßende entspricht. Dieses Fördervolumen wird nicht dadurch verkleinert, daß die Steigung sofort abnimmt. Vorteilhafterweise erstreckt sich der Bereich mit konstanter Steigung am Einlaßende über mindestens eine Windung (360°). Auch am Auslaßende ist wieder eine konstante Steigung vorgesehen, die kleiner ist als die Steigung am Einlaßende. Dadurch werden die erwähnten Probleme der Rückströmung sehr stark vermindert, da über eine Windung oder sogar mehrere Windungen im wesentlichen konstanter Druck herrscht. Dadurch wird auch der Enddruck der Pumpe vermindert. Gleichzeitig wird wegen des kleineren Fördervolumens die Leistungsaufnahme vermindert.The slope is therefore constant at the inlet end. That’s why original delivery volume the size of the slope on Inlet end corresponds. This funding volume will not reduced that the slope decreases immediately. Advantageously extends the area with constant slope at least one turn (360 °) at the inlet end. Also a constant slope is again provided at the outlet end, which is less than the slope at the inlet end. This will the mentioned problems of backflow are greatly reduced, because over one turn or even several turns in the there is essentially constant pressure. This also makes the Final pressure of the pump reduced. At the same time because of the smaller funding volume reduces the power consumption.

Zwischen den beiden Bereichen mit konstanten Steigungen befindet sich der Abschnitt, in dem die Steigung am Einlaßende auf die deutlich kleinere Steigung am Auslaßende reduziert wird. Dieser Verlauf ist unter thermodynamischen Aspekten der günstigste.Located between the two areas with constant gradients the section where the slope at the inlet end reduced to the much smaller slope at the outlet end becomes. This course is the thermodynamic aspects of best.

Es sind zwar Verdrängermaschinen bekannt bei denen die Rotoren am Einlaßende und Auslaßende jeweils konstante Steigungen aufweisen (GB 2 227 057 B, EP 0 183 380 B1). Diese Verdrängermaschinen sind aber zum Fördern von Flüssigkeiten vorgesehen, die Gaseinschlüsse enthalten können. Da Flüssigkeiten nicht in nennenswertem Maße komprimierbar sind, müssen die Spaltweiten zwischen den Rotoren und der Wand des Förderraums so dimensioniert werden, daß Flüssigkeit während der Komprimierung durch die Spalte entsprechend der Druckdifferenz zurück zur Einlaßseite strömen kann. Damit trotzdem eine vernünftige Pumpwirkung erreicht wird, sind am Einlaßende und Auslaßende Bereiche mit konstanter Steigung vorgesehen, die die Flüssigkeit normal ohne Komprimierung fördern, da sonst wegen der erwähnten erforderlichen großen Spaltbreiten keine vernünftige Pumpwirkung erzielt werden könnte. Da diese Pumpen gattungsfremd sind und die Problematik bei der Förderung von Flüssigkeit völlig anders ist als bei kompressiblen Medien, vermögen diese Pumpen keinerlei Hinweise in Richtung auf die erfindungsgemäßen Verdrängermaschinen zu geben.There are displacement machines in which the rotors are known constant slopes at the inlet end and outlet end have (GB 2 227 057 B, EP 0 183 380 B1). These displacement machines are intended for the conveyance of liquids, which may contain gas inclusions. Because liquids are not compressible to any significant degree, the Gaps between the rotors and the wall of the delivery room be dimensioned so that liquid during compression through the column corresponding to the pressure difference can flow to the inlet side. So it's still a reasonable one Pumping action is achieved at the inlet end and Outlet areas with constant slope provided pump the liquid normally without compression, otherwise none due to the large gap widths required reasonable pumping action could be achieved. Because these pumps are alien and the problem with funding of liquid is completely different from that of compressible media, these pumps are unable to provide any indication of to give the displacement machines according to the invention.

Außerdem sind die Rotoren der vorbekannten Verdrängermaschinen soweit ersichtlich eingängig. Bei der erfindungsgemäßen Verdrängermaschine sind die schraubenförmigen Rotoren zweigängig, um besser ausgewuchtet werden zu können, was für hohe Drehgeschwindigkeiten unbedingt erforderlich ist. Außerdem ist die Wärmeabfuhr durch die besser verteilten Spaltströme erhöht. Diese Wärmeabfuhr ist bei den flüssigkeitsfördernden Verdrängermaschinen des Standes der Technik nicht problematisch.In addition, the rotors of the known displacement machines as far as can be seen catchy. In the case of the invention Displacement machine, the helical rotors have two gears, to be better balanced, what high Rotational speeds is absolutely necessary. Moreover is the heat dissipation through the better distributed gap currents elevated. This heat dissipation is with the liquid-promoting Displacement machines of the prior art are not problematic.

Vorteilhafterweise sind die Steigungen am Einlaß- und Auslaßende über mindestens eine Windung konstant. Für die Komprimierung von Gasen bzw. die Erzielung eines guten Vakuums ist es besonders vorteilhaft, wenn die Steigung am Auslaßende über mindestens zwei Windungen konstant ist. Dadurch erhält man nicht nur eine bessere Abdichtung und geringere Rückströmung, sondern auch eine bessere Abführung der Verdichtungswärme. Bei einer trockenlaufenden Vakuumpumpe entstehen dann die Verdichtungswärme durch die Volumenverkleinerung und die Verdichtungswärme durch das Eindringen von Außenluft am Auslaßende nicht mehr an der selben Stelle und können daher besser abgeführt werden. Advantageously, the slopes are at the inlet and outlet ends constant over at least one turn. For compression of gases or achieving a good vacuum it is particularly advantageous if the slope at the outlet end is constant over at least two turns. This gives you not only get better sealing and less backflow, but also better dissipation of the heat of compression. This then arises with a dry-running vacuum pump the heat of compression through the volume reduction and Heat of compression due to the penetration of outside air at the outlet end no longer in the same place and can therefore do better be dissipated.

Die Zahl der Windungen, über die die Steigung konstant ist, hängt von den gewünschten Betriebsbedingungen der Pumpe ab.The number of turns over which the slope is constant depends on the desired operating conditions of the pump.

Ein besonders günstiges Verhalten der Verdrängermaschine insbesondere im Vakuumbereich wird erhalten, wenn vorgesehen ist, daß die Wellen jeweils durch eigene Elektromotoren angetrieben werden, wobei die Winkelpositionen der Wellen mit Resolvern bestimmt werden, aufgrund von deren Signalen die Motoren elektronisch synchronisiert werden, und wobei die Wellen Zahnräder aufweisen, die ineinandergreifen und deren Winkelspiel kleiner ist als dasjenige der Profilkörper. Die Rotoren werden also nicht über Getriebe angetrieben, sondern werden vollständig berührungsfrei durch eigene Elektromotoren angetrieben, wobei die Zahnräder lediglich den Zweck haben, bei Ausfall der elektronischen Synchronisation zu verhindern, daß sich die empfindlichen Oberflächen der Rotoren berühren und beschädigt werden. Statt dessen werden sich zunächst die Zahnräder berühren, was keine Probleme bereitet, insbesondere, wenn diese mit entsprechender Oberfläche versehen sind.A particularly favorable behavior of the displacement machine in particular in the vacuum range is obtained if provided is that the shafts are each driven by their own electric motors be, the angular positions of the shafts with resolvers the motors are determined on the basis of their signals be electronically synchronized, and being the waves Have gears that mesh and their angular play is smaller than that of the profile body. The rotors are not driven by gears, but are completely contact-free thanks to our own electric motors driven, the gears only have the purpose prevent in the event of failure of the electronic synchronization, that the sensitive surfaces of the rotors touch and get damaged. Instead, the Touch gears, which is not a problem, in particular, if they are provided with the appropriate surface.

Wenn eine Differenzregelung für die Drehzahl der Motoren vorgesehen ist, wird die Pumpfähigkeit und Zuverlässigkeit der Pumpe weiter erhöht. Dringt zum Beispiel Flüssigkeit in die Pumpe ein, so werden beide Rotoren gleichförmig beeinflußt; die Differenz wird sich nur wenig ändern. Würde man dagegen die Regelung auf einen vorgegebenen Wert unabhängig für beide Rotoren durchführen, so müßten an beiden Rotoren sehr große Geschwindigkeitsänderungen vorgenommen werden, wenn die Rotoren durch eindringende Flüssigkeit plötzlich abgebremst werden. If a differential control is provided for the speed of the motors is, the pumpability and reliability of the Pump further increased. For example, liquid penetrates into the Pump on, both rotors are influenced uniformly; the difference will change little. Would you mind regulation to a predetermined value independently for both Perform rotors, so would have to be very large on both rotors Speed changes are made when the rotors can suddenly be slowed down by penetrating liquid.

Als besonders zweckmäßig für den Betrieb haben sich Drehstrommotoren mit permanent magnetischem Rotor als Antrieb erwiesen.Three-phase motors have proven to be particularly suitable for operation proven with permanent magnetic rotor as drive.

Die Erfindung wird im folgenden anhand einer vorteilhaften Ausführungsform unter Bezugnahme auf die beigefügten Zeichnungen beschrieben. Es zeigen:

Fig 1.
schematisch den Aufbau einer Verdrängermaschine, bei der die Erfindung verwendet werden kann; und
Fig 2.
erfindungsgemäße Profilkörper, die im Zusammenhang mit der Verdrängermaschine der Figur 1 verwendet werden können.
The invention is described below using an advantageous embodiment with reference to the accompanying drawings. Show it:
Fig. 1.
schematically the structure of a displacement machine in which the invention can be used; and
Fig. 2.
Profile body according to the invention, which can be used in connection with the displacement machine of Figure 1.

Wie dies in Fig. 1 gezeigt ist, sind in einem aus mehreren Teilen aufgebauten Pumpengehäuse 1 mit Lagern 2 zwei Wellen 3 gelagert, auf denen Profilkörper 4 befestigt sind, die ineinandergreifen und im Pumpenraum 5 durch einen Anschluß 13 das zu fördernde Medium von oben ansaugen und unten durch nicht gezeigte Öffnungen ausstoßen. Die Wellen 3 und die Profilkörper 4 werden durch Elektromotoren 6 angetrieben, wobei für jede Welle 3 ein separater Elektromotor 6 vorgesehen ist. Unten an den Wellen 3 sind zwei ineinandergreifende Zahnräder 7 vorgesehen. Die Motoren 6 werden mit Hilfe von Resolvern 8 elektronisch synchronisiert. Bei widrigen Betriebsbedingungen, wenn die elektronische Synchronisation nicht ausreicht, berühren sich zunächst die Zahnräder 7, da sie ein geringeres Winkelspiel als die Rotoren 4 aufweisen. Normalerweise berühren sich aber die Zahnräder 7 nicht, so daß auf eine Schmierung dieser Zahnräder verzichtet werden kann. As shown in Fig. 1, there are one of several Parts of assembled pump housing 1 with bearings 2 two shafts 3 stored on which profile body 4 are attached, which interlock and in the pump chamber 5 through a connection 13 that Suck the medium to be pumped from above and not through the bottom Eject the openings shown. The waves 3 and the profile body 4 are driven by electric motors 6, whereby for each shaft 3 a separate electric motor 6 is provided. Below there are two intermeshing gear wheels 7 on the shafts 3 intended. The motors 6 are made using resolvers 8 electronically synchronized. In adverse operating conditions, if the electronic synchronization is not sufficient, first touch the gears 7 because they are one have less angular play than the rotors 4. Usually but do not touch the gears 7, so that lubrication of these gears can be dispensed with.

In Fig. 2 sind erfindungsgemäße Rotoren gezeigt, bei denen die Steigung von oben (Einlaßende) nach unten (Auslaßende) abnimmt. Im Einlaßbereich hat die Steigung S1 über mindestens eine Windung einen konstanten Wert. Das gleiche gilt für die Steigung S3 am Auslaßende, die dort ebenfalls konstant ist, aber wesentlich kleiner als die Steigung S1 am Einlaßende. Der Bereich konstanter Steigung S3 erstreckt sich dabei vorteilhafterweise über mindestens zwei Windungen der Rotoren 4. Zwischen Einlaßende mit Steigung S1 und Auslaßende mit Steigung S3 ändert sich die Steigung S2 kontinuierlich vom Wert von S1 zum Wert von S3.In Fig. 2 rotors according to the invention are shown, in which the slope decreases from the top (inlet end) to the bottom (outlet end). In the inlet area, the slope S 1 has a constant value over at least one turn. The same applies to the slope S 3 at the outlet end, which is also constant there, but much smaller than the slope S 1 at the inlet end. The range of constant slope S 3 advantageously extends over at least two turns of the rotors 4. Between the inlet end with slope S 1 and the outlet end with slope S 3 , the slope S 2 changes continuously from the value of S 1 to the value of S 3 .

Claims (6)

Verdrängermaschine für kompressible Medien, insbesondere trockenlaufende Vakuumpumpe, mit mindestens zwei Wellen (3) mit Rotoren (4), die als schraubenförmige Profilkörper (4) ausgebildet sind und deren Profile bei der Drehung zahnradartig ineinandergreifen und berührungsfrei zueinander laufen, wobei die Steigung der schraubenförmigen Profilkörper vom Einlaß zum Auslaß abnimmt, dadurch gekennzeichnet, daß die schraubenförmigen Profilkörper (4) zweitgängig ausgebildet sind und daß die Steigungen (S1, S3) am Einlaßende und Auslaßende der schraubenförmigen Profilkörper (4) konstant sind und dazwischen von der größeren Steigung (S1) am Einlaßende zur kleineren Steigung (S3) am Auslaßende die Steigung (S2) kontinuierlich abnimmt.Displacement machine for compressible media, in particular dry-running vacuum pump, with at least two shafts (3) with rotors (4), which are designed as helical profile bodies (4) and whose profiles mesh with each other during rotation and run without contact with one another, the pitch of the helical profile bodies decreases from the inlet to the outlet, characterized in that the helical profile bodies (4) are of two-pass design and that the slopes (S 1 , S 3 ) at the inlet end and outlet end of the helical profile bodies (4) are constant and between them from the larger slope (S 1 ) at the inlet end to the smaller slope (S 3 ) at the outlet end the slope (S 2 ) decreases continuously. Verdrängermaschine nach Anspruch 1, dadurch gekennzeichnet, daß die Steigung (S1, S3) am Einlaß- und Auslaßende über mindestens eine Windung konstant sind.Displacement machine according to claim 1, characterized in that the slope (S 1 , S 3 ) at the inlet and outlet ends are constant over at least one turn. Verdrängermaschine nach Anspruch 2, dadurch gekennzeichnet, daß die Steigung (S3) am Auslaßende über mindestens zwei Windungen konstant ist.Displacement machine according to claim 2, characterized in that the slope (S 3 ) at the outlet end is constant over at least two turns. Verdrängermaschine nach den Ansprüchen 1 bis 3, dadurch gekennzeichnet, daß die Wellen (3) jeweils durch eigene Elektromotoren (6) angetrieben werden, wobei die Winkelpositionen der Wellen (3) mit Resolvern (8) bestimmt werden, aufgrund von deren Signalen die Motoren (6) elektronisch synchronisiert werden, und wobei die Wellen (3) Zahnräder (7) aufweisen, die ineinandergreifen und deren Winkelspiel kleiner ist als dasjenige der Profilkörper (4).Displacement machine according to claims 1 to 3, characterized characterized in that the shafts (3) each have their own Electric motors (6) are driven, the angular positions the waves (3) with resolvers (8) determined based on their signals, the motors (6) be electronically synchronized, and being the waves (3) have gears (7) which mesh and whose angular play is smaller than that Profile body (4). Verdrängermaschine nach den Ansprüchen 1 bis 4, dadurch gekennzeichnet, daß sie eine Differenzregelung für die Drehzahl der Motoren (6) aufweist.Displacement machine according to claims 1 to 4, characterized characterized in that it is a differential scheme for the Revs of the motors (6). Verdrängermaschine nach den Ansprüchen 1 bis 5, dadurch gekennzeichnet, daß die Motoren (6) Drehstrommotoren mit permanent magnetischem Rotor sind.Displacement machine according to claims 1 to 5, characterized characterized in that the motors (6) three-phase motors with permanent magnetic rotor.
EP99114031A 1999-07-19 1999-07-19 Positive displacement machine for compressible fluids Expired - Lifetime EP1070848B1 (en)

Priority Applications (13)

Application Number Priority Date Filing Date Title
DK99114031T DK1070848T3 (en) 1999-07-19 1999-07-19 Compressible media displacement machine
AT99114031T ATE264457T1 (en) 1999-07-19 1999-07-19 DISPLACEMENT MACHINE FOR COMPRESSIBLE MEDIA
DE59909182T DE59909182D1 (en) 1999-07-19 1999-07-19 Displacement machine for compressible media
ES99114031T ES2219956T3 (en) 1999-07-19 1999-07-19 VOLUMETRIC MACHINE FOR COMPRESSIBLE MEDIA.
EP99114031A EP1070848B1 (en) 1999-07-19 1999-07-19 Positive displacement machine for compressible fluids
NO20003590A NO323484B1 (en) 1999-07-19 2000-07-13 Compressible media displacement machine
ZA200003568A ZA200003568B (en) 1999-07-19 2000-07-17 Displacement machine for compressible media.
KR1020000041054A KR100573752B1 (en) 1999-07-19 2000-07-18 Displacement machine for compressible media
JP2000217626A JP2001055992A (en) 1999-07-19 2000-07-18 Compressive medium discharger
SG200003980A SG86422A1 (en) 1999-07-19 2000-07-18 Displacement machine for compressible media
CA002314124A CA2314124C (en) 1999-07-19 2000-07-18 Displacement machine for compressible media
AU48703/00A AU775135B2 (en) 1999-07-19 2000-07-19 Displacement machine for compressible media
US09/619,600 US6359411B1 (en) 1999-07-19 2000-07-19 Displacement machine for compressible media

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP99114031A EP1070848B1 (en) 1999-07-19 1999-07-19 Positive displacement machine for compressible fluids

Publications (2)

Publication Number Publication Date
EP1070848A1 true EP1070848A1 (en) 2001-01-24
EP1070848B1 EP1070848B1 (en) 2004-04-14

Family

ID=8238616

Family Applications (1)

Application Number Title Priority Date Filing Date
EP99114031A Expired - Lifetime EP1070848B1 (en) 1999-07-19 1999-07-19 Positive displacement machine for compressible fluids

Country Status (13)

Country Link
US (1) US6359411B1 (en)
EP (1) EP1070848B1 (en)
JP (1) JP2001055992A (en)
KR (1) KR100573752B1 (en)
AT (1) ATE264457T1 (en)
AU (1) AU775135B2 (en)
CA (1) CA2314124C (en)
DE (1) DE59909182D1 (en)
DK (1) DK1070848T3 (en)
ES (1) ES2219956T3 (en)
NO (1) NO323484B1 (en)
SG (1) SG86422A1 (en)
ZA (1) ZA200003568B (en)

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6702558B2 (en) 2000-07-25 2004-03-09 Ateliers Busch Sa Twin screw rotors and displacement machines containing the same
DE102010019402A1 (en) * 2010-05-04 2011-11-10 Oerlikon Leybold Vacuum Gmbh Screw vacuum pump
CN102808771A (en) * 2012-08-14 2012-12-05 东北大学 Single-head varying-pitch screw rotor with equal tooth top width
CN103486023A (en) * 2013-07-10 2014-01-01 重庆德衡科技有限公司 Screw pump and screw
WO2014001089A1 (en) * 2012-06-28 2014-01-03 Sterling Industry Consult Gmbh Screw pump
WO2013175019A3 (en) * 2012-05-25 2014-06-12 Ateliers Busch Sa Improved screw‑type positive displacement machine
EP2204532A3 (en) * 2008-12-31 2014-10-08 General Electric Company Positive displacement gas turbine engine with parallel screw rotors
DE202016005209U1 (en) * 2016-08-30 2017-12-01 Leybold Gmbh Screw vacuum pump
DE102016216279A1 (en) 2016-08-30 2018-03-01 Leybold Gmbh Vacuum-screw rotor
DE202017005336U1 (en) * 2017-10-17 2019-01-21 Leybold Gmbh screw rotor

Families Citing this family (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2004263629A (en) * 2003-03-03 2004-09-24 Tadahiro Omi Screw vacuum pump
GB0405527D0 (en) * 2004-03-12 2004-04-21 Boc Group Plc Vacuum pump
TWI281531B (en) * 2004-06-15 2007-05-21 Toyota Ind Corp Screw pump and screw gear
JP4839443B2 (en) 2004-06-18 2011-12-21 国立大学法人東北大学 Screw vacuum pump
JP4853168B2 (en) * 2006-08-10 2012-01-11 株式会社豊田自動織機 Screw pump
JP4779868B2 (en) 2006-08-11 2011-09-28 株式会社豊田自動織機 Screw pump
US20080193316A1 (en) * 2007-02-08 2008-08-14 Kabushiki Kaisha Toyota Jidoshokki Roots pump
RU2448273C2 (en) * 2009-08-03 2012-04-20 Открытое акционерное общество "УРАЛЬСКИЙ ЭЛЕКТРОХИМИЧЕСКИЙ КОМБИНАТ" Rotary screw machine
KR101138389B1 (en) * 2009-10-21 2012-04-26 주식회사 코디박 Screw rotor type vaccum pump with built in motor
KR101142113B1 (en) * 2009-10-21 2012-05-09 주식회사 코디박 Motor and rotor shaft one body type screw rotor vaccum pump
KR101150971B1 (en) * 2009-10-22 2012-06-01 주식회사 코디박 Screw rotor type vaccum pump
US8764424B2 (en) 2010-05-17 2014-07-01 Tuthill Corporation Screw pump with field refurbishment provisions
CN104454523B (en) * 2014-11-25 2016-07-20 巫修海 A kind of screw rod of screw vacuum pump
CN106151031A (en) * 2016-09-30 2016-11-23 北京艾岗科技有限公司 A kind of oil free screw air compressor machine
DE202018000178U1 (en) * 2018-01-12 2019-04-15 Leybold Gmbh compressor

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH246525A (en) * 1942-05-21 1947-01-15 Graaf George Alexander V D Vacuum pump, which has several interlocking feed screws.
FR1500160A (en) * 1966-07-29 1967-11-03 Improvements to compressors and rotary motors
GB2165890A (en) * 1984-10-24 1986-04-23 Stothert & Pitt Plc Postive displacement screw pumps
DE19749572A1 (en) * 1997-11-10 1999-05-12 Peter Dipl Ing Frieden Vacuum pump or dry running screw compactor
DE19800825A1 (en) * 1998-01-02 1999-07-08 Schacht Friedrich Dry compacting screw pump

Family Cites Families (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB165890A (en) 1920-02-03 1921-06-03 Frank Henry Trier Improvements in tunnelling machines
CH635403A5 (en) * 1978-09-20 1983-03-31 Edouard Klaey SCREW MACHINE.
US4792295A (en) * 1987-03-05 1988-12-20 Joyce Sr Benjamin N Variable volume rotary vane pump-motor units
FR2647853A1 (en) * 1989-06-05 1990-12-07 Cit Alcatel DRY PRIMARY PUMP WITH TWO FLOORS
DE69123898T3 (en) * 1990-08-01 2004-08-05 Matsushita Electric Industrial Co., Ltd., Kadoma Rotary system for liquid media
US5108275A (en) * 1990-12-17 1992-04-28 Sager William F Rotary pump having helical gear teeth with a small angle of wrap
KR960009860B1 (en) * 1992-01-31 1996-07-24 다니이 아끼오 Synchronous rotating apparatus for rotating a plurality of shafts
JP3569924B2 (en) * 1992-03-19 2004-09-29 松下電器産業株式会社 Fluid rotating device
US5374173A (en) * 1992-09-04 1994-12-20 Matsushita Electric Industrial Co., Ltd. Fluid rotating apparatus with sealing arrangement
DE4314418A1 (en) * 1993-05-03 1994-11-10 Leybold Ag Friction vacuum pump with differently designed pump sections
DE4318707A1 (en) * 1993-06-04 1994-12-08 Sihi Gmbh & Co Kg Displacement machine with electronic motor synchronization
JPH08100779A (en) * 1994-10-04 1996-04-16 Matsushita Electric Ind Co Ltd Vacuum pump
US5704250A (en) * 1996-04-04 1998-01-06 Western Atlas, Inc. Ball screw drive with dynamically adjustable preload

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH246525A (en) * 1942-05-21 1947-01-15 Graaf George Alexander V D Vacuum pump, which has several interlocking feed screws.
FR1500160A (en) * 1966-07-29 1967-11-03 Improvements to compressors and rotary motors
GB2165890A (en) * 1984-10-24 1986-04-23 Stothert & Pitt Plc Postive displacement screw pumps
DE19749572A1 (en) * 1997-11-10 1999-05-12 Peter Dipl Ing Frieden Vacuum pump or dry running screw compactor
DE19800825A1 (en) * 1998-01-02 1999-07-08 Schacht Friedrich Dry compacting screw pump

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6702558B2 (en) 2000-07-25 2004-03-09 Ateliers Busch Sa Twin screw rotors and displacement machines containing the same
EP2204532A3 (en) * 2008-12-31 2014-10-08 General Electric Company Positive displacement gas turbine engine with parallel screw rotors
DE102010019402A1 (en) * 2010-05-04 2011-11-10 Oerlikon Leybold Vacuum Gmbh Screw vacuum pump
WO2013175019A3 (en) * 2012-05-25 2014-06-12 Ateliers Busch Sa Improved screw‑type positive displacement machine
WO2014001089A1 (en) * 2012-06-28 2014-01-03 Sterling Industry Consult Gmbh Screw pump
CN102808771A (en) * 2012-08-14 2012-12-05 东北大学 Single-head varying-pitch screw rotor with equal tooth top width
CN103486023A (en) * 2013-07-10 2014-01-01 重庆德衡科技有限公司 Screw pump and screw
CN103486023B (en) * 2013-07-10 2015-10-28 重庆德衡科技有限公司 Screw pump and screw rod
DE202016005209U1 (en) * 2016-08-30 2017-12-01 Leybold Gmbh Screw vacuum pump
DE102016216279A1 (en) 2016-08-30 2018-03-01 Leybold Gmbh Vacuum-screw rotor
DE202017005336U1 (en) * 2017-10-17 2019-01-21 Leybold Gmbh screw rotor

Also Published As

Publication number Publication date
AU775135B2 (en) 2004-07-15
KR100573752B1 (en) 2006-04-24
DE59909182D1 (en) 2004-05-19
US6359411B1 (en) 2002-03-19
ES2219956T3 (en) 2004-12-01
DK1070848T3 (en) 2004-08-09
NO323484B1 (en) 2007-05-21
CA2314124A1 (en) 2001-01-19
EP1070848B1 (en) 2004-04-14
KR20010015358A (en) 2001-02-26
ATE264457T1 (en) 2004-04-15
ZA200003568B (en) 2001-02-07
NO20003590L (en) 2001-01-22
AU4870300A (en) 2001-01-25
JP2001055992A (en) 2001-02-27
CA2314124C (en) 2008-05-27
SG86422A1 (en) 2002-02-19
NO20003590D0 (en) 2000-07-13

Similar Documents

Publication Publication Date Title
EP1070848B1 (en) Positive displacement machine for compressible fluids
DE60034006T2 (en) Device for evacuating a vacuum system
DE3711143A1 (en) TWO-STAGE VACUUM PUMP DEVICE
DE3422389A1 (en) FLOWING MACHINE IN SPIRAL DESIGN
DE2242269A1 (en) GEAR PUMP OR MOTOR
CH495509A (en) Screw machine
DE2553222C3 (en) Adjustable screw compressor
DE2033201A1 (en) Displacement machine with helical displacement bodies
DE4005749A1 (en) SPIRAL COMPRESSOR OR DISPLACEMENT
DE69928172T2 (en) Vacuum pump
EP1073845B1 (en) Positive displacement machine
EP0094379A1 (en) Rotary pump for delivering gases and liquids, particulary for use as a driving unit for blood diaphragm pumps
EP1061260A1 (en) Positive displacement machine for compressible fluids
DE10159147A1 (en) Hydraulic gear pump has pump stages in one plane, one above other radially
DE4134965A1 (en) SPIRAL COMPRESSOR WITH MODIFIED HEAD
EP0539673B1 (en) Internal gear pump with two ring gears and one common pinion
DE4421255C1 (en) Packing pieceless inner gearwheel pump
EP3961035A1 (en) Method and screw spindle pump for supplying a gas-liquid mix
EP0578853B1 (en) Rotary machine with conjugated profiles in continuous contact
DE2134241C3 (en) Two-stage external-axis rotary piston machine
DE3045192C2 (en) Gear pump
DE1428270B2 (en) Screw compressor with screw rotors rotating in meshing engagement
DE3118297A1 (en) GEAR PUMP
DE3737961A1 (en) Internal-gear pump
EP1509698A1 (en) Variable volume flow internal gear pump

Legal Events

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

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AT BE CH CY DE DK ES FI FR GB GR IE IT LI LU MC NL PT SE

AX Request for extension of the european patent

Free format text: AL;LT;LV;MK;RO;SI

17P Request for examination filed

Effective date: 20010627

AKX Designation fees paid

Free format text: AT BE CH CY DE DK ES FI FR GB GR IE IT LI LU MC NL PT SE

17Q First examination report despatched

Effective date: 20030401

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AT BE CH CY DE DK ES FI FR GB GR IE IT LI LU MC NL PT SE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20040414

Ref country code: CY

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20040414

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

REF Corresponds to:

Ref document number: 59909182

Country of ref document: DE

Date of ref document: 20040519

Kind code of ref document: P

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

Free format text: GERMAN

REG Reference to a national code

Ref country code: SE

Ref legal event code: TRGR

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20040714

REG Reference to a national code

Ref country code: CH

Ref legal event code: NV

Representative=s name: TROESCH SCHEIDEGGER WERNER AG

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LU

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20040719

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MC

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20040731

REG Reference to a national code

Ref country code: DK

Ref legal event code: T3

GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)

Effective date: 20040719

REG Reference to a national code

Ref country code: ES

Ref legal event code: FG2A

Ref document number: 2219956

Country of ref document: ES

Kind code of ref document: T3

ET Fr: translation filed
PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

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

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed

Effective date: 20050117

ET1 Fr: translation filed ** revision of the translation of the patent or the claims
PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: PT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20040914

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: IE

Payment date: 20090727

Year of fee payment: 11

Ref country code: FR

Payment date: 20090720

Year of fee payment: 11

Ref country code: ES

Payment date: 20090724

Year of fee payment: 11

Ref country code: DK

Payment date: 20090723

Year of fee payment: 11

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: SE

Payment date: 20090727

Year of fee payment: 11

Ref country code: NL

Payment date: 20090724

Year of fee payment: 11

Ref country code: GB

Payment date: 20090724

Year of fee payment: 11

Ref country code: CH

Payment date: 20090727

Year of fee payment: 11

Ref country code: AT

Payment date: 20090723

Year of fee payment: 11

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: BE

Payment date: 20090728

Year of fee payment: 11

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: IT

Payment date: 20090728

Year of fee payment: 11

BERE Be: lapsed

Owner name: *STERLING FLUID SYSTEMS (GERMANY) G.M.B.H.

Effective date: 20100731

REG Reference to a national code

Ref country code: NL

Ref legal event code: V1

Effective date: 20110201

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20100719

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20110331

REG Reference to a national code

Ref country code: IE

Ref legal event code: MM4A

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20100731

Ref country code: CH

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20100731

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: NL

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20110201

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20100802

Ref country code: AT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20100719

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20100719

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: BE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20100731

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20100719

Ref country code: IE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20100719

REG Reference to a national code

Ref country code: ES

Ref legal event code: FD2A

Effective date: 20110818

REG Reference to a national code

Ref country code: DK

Ref legal event code: EBP

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: ES

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20100720

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DK

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20100802

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20100720

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20180727

Year of fee payment: 20

REG Reference to a national code

Ref country code: DE

Ref legal event code: R071

Ref document number: 59909182

Country of ref document: DE