EP1957798A1 - Helical screw compressor - Google Patents

Helical screw compressor

Info

Publication number
EP1957798A1
EP1957798A1 EP06762002A EP06762002A EP1957798A1 EP 1957798 A1 EP1957798 A1 EP 1957798A1 EP 06762002 A EP06762002 A EP 06762002A EP 06762002 A EP06762002 A EP 06762002A EP 1957798 A1 EP1957798 A1 EP 1957798A1
Authority
EP
European Patent Office
Prior art keywords
rotor
profile
rotors
ribs
screw compressor
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
EP06762002A
Other languages
German (de)
French (fr)
Other versions
EP1957798B1 (en
Inventor
Carsten Achtelik
Dieter HÜTTERMANN
Michael Besseling
Norbert Henning
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.)
GHH Rand Schraubenkompressoren GmbH
Original Assignee
GHH Rand Schraubenkompressoren 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 GHH Rand Schraubenkompressoren GmbH filed Critical GHH Rand Schraubenkompressoren GmbH
Publication of EP1957798A1 publication Critical patent/EP1957798A1/en
Application granted granted Critical
Publication of EP1957798B1 publication Critical patent/EP1957798B1/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

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
    • 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
    • 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
    • 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
    • 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
    • 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

Abstract

The invention relates to a helical screw compressor which comprises two rotors (7, 9) having ribs (7', 9) which extend a screw-like manner and grooves which engage with each other in a combing and sealing manner. The total number of ribs of both rotors is at least 14, and the height (H) of the grooves is no more than 0,15 times the external diameter (Da) of the rotor profile (7) and/or (9). The shaft journals of the rotors have a diameter which is not smaller than half of the external diameter (Da) of the rotor profile.

Description

Schraubenkompressor  Screw compressor
Die Erfindung betrifft einen Schraubenkompressor mit zwei in einem Rotorgehäuse achsparallel drehbar gelagerten Schraubenrotoren, von denen jeder einen Profϊlabschnitt 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. The invention relates to a screw compressor with two screw rotors which are rotatably mounted axially parallel in a rotor housing, each of which has a profile section with helically running ribs and grooves. The rotors intermesh with their ribs and grooves in a meshing and sealing manner, and in operation gas volumes enclosed between them and the rotor housing are conveyed and compressed.
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. When designing the profiles of such screw rotors, efforts have hitherto been made to provide the largest possible volumes for the gas volume to be compressed, which is enclosed between the rotors and the rotor housing, given the outer diameter of the rotor profiles. H. to achieve the greatest possible volumetric utilization of the rotor profile.
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. In contrast, the present invention aims to provide a screw compressor which is suitable for compressing gas to very high pressures, typically in the range from 30 to 50 bar, and which is in particular the last stage of a multi-stage, in particular three-stage Compressor unit can be operated. At such high pressures, the rotors are exposed to strong transverse axial forces due to the gas volume enclosed between them and the housing under high pressure, which act in the sense of a deflection of the rotors. This can impair the seal between the rotors and thus lead to a loss in efficiency. Also, due to the deflection of the rotors, the radial gap between the rotors and the rotor housing cannot be dimensioned as small as would be desirable to achieve a good seal 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.
Die erfindungsgemäße Lösung der Aufgabe ist im Anspruch 1 angegeben. Die Unteransprüche beziehen sich auf vorteilhafte weitere Ausgestaltungen der Erfindung. The achievement of the object is specified in claim 1. The subclaims relate to advantageous further refinements of the invention.
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. It was found that the design of the rotors specified in the claims leads to a particularly favorable ratio between the bending stiffness of the rotors on the one hand and the size of the compressed gas volume enclosed in the screw grooves of the rotors, which causes the bending forces.
Eine Ausführungsform der Erfindung wird im Folgenden anhand der Zeichnungen näher erläutert. Es zeigt An embodiment of the invention is explained in more detail below with reference to the drawings. It shows
Figur 1 eine teilweise geschnittene Ansicht eines erfindungsgemäßen Schraubenkompressors. Figure 1 is a partially sectioned view of a screw compressor according to the invention.
Figur 2 eine perspektivische Darstellung der Rotoren des Schraubenkompressors gemäß Figur 1.  FIG. 2 shows a perspective illustration of the rotors of the screw compressor according to FIG. 1.
Figur 3 das Rotorprofϊl der beiden Rotoren im achssenkrechten Querschnitt.  Figure 3 shows the rotor profile of the two rotors in the perpendicular cross section.
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 1 1 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. - J - The screw compressor shown as an exemplary embodiment in FIG. 1 has a rotor housing 1, shown in section, in which two rotors 3 and 5 are rotatably mounted in parallel axes. The axes of rotation of the rotors 3, 5 lie in a common vertical plane, which is also the sectional 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, the ribs and grooves of the two profile sections 7, 9 intermeshing. Shaft journals 7a, 7b, 9a, 9b adjoin the profile sections 7, 9, and sealing rings 11 cooperate with their circumferential surface in order to seal the rotor in the rotor housing 1. The shaft journals 7a, 7b, 9a, 9b are also rotatably supported in the rotor housing 1 by bearings 13, 15. - J -
Der in Figur 1 obere Rotor 3 ist der Hauptläufer und weist an seinem in Figur 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 in Figur 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. The upper rotor 3 in FIG. 1 is the main rotor and has at its left end in FIG. 1 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 to rotate. At the right end in FIG. 1, the two rotors 3, 5 have two meshing gears 17, 19 which form a synchronizing gear which rotates from the upper rotor 3 to the lower rotor 5, which is the secondary rotor, in the desired speed ratio transmits and ensures that the profile sections 7, 9 of the rotors mesh without contact.
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 1 1 abgedichteten Bereichs, z. B. zur Schmierung des (nicht dargestellten) Antriebsgetriebes, der Lager 13, 15 und des Gleichlaufgetriebes 17, 19 zugeführt. The screw compressor described is preferably dry-running, ie no oil is supplied to the compressor chamber for lubrication, cooling or sealing. The rotor profiles engage in a contact-free and yet sealing manner. This is advantageous for all applications in which it is important that the compressed gas is completely free of oil. Oil is only outside the compressor room, i.e. H. outside the area sealed by the seals 1 1, e.g. B. for lubricating the (not shown) drive gear, the bearings 13, 15 and the synchronous gear 17, 19 supplied.
In Figur 2 sind die beiden Rotoren 3, 5 des Schraubenkompressors von Figur 1 gesondert perspektivisch dargestellt. Man erkennt aus Figur 2, dass der Rotor 3, der der Hauptläufer ist, einen Profilabschnitt 7 aufweist, dessen Profil von sechs schraubenförmig verlaufenden Rippen T 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. In Figure 2, the two rotors 3, 5 of the screw compressor of Figure 1 are shown separately in perspective. It can be seen from FIG. 2 that the rotor 3, which is the main rotor, has a profile section 7, the profile of which is formed by six helically running ribs T. The lower rotor 5, which is the secondary rotor, has a profile section 9 with a profile which is formed by eight helically running ribs 9 '. The sum of the numbers of the helical ribs 7 ', 9' of the two rotors, i. H. the sum of the "number of teeth" is 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 T auf, die durch Nuten 7" voneinander getrennt sind. Die Kopfflächen der Rippen T 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. Also shown in FIG. 2 are the areas 7a, 7b, 9a, 9b of the shaft journals with a diameter (D, D ') which adjoin the profile section 7 or 9 of each of the rotors 3, 5 on both sides and which have a diameter (D, D') which is more than half the outer diameter of the respective profile section. Figure 3 shows the profile sections 7, 9 of the two rotors in the axial section. The profile 7 of the main rotor has six helical ribs T, which are separated from one another by grooves 7 ". The top surfaces of the ribs T lie on the outer enveloping circle Ka of the profile with the diameter Da. The bottom surfaces of the grooves 7" lie on the inner circle Ki with the diameter Di. The radial distance between the circles Ka and Ki is called the rib height or tooth height H. This is not larger, preferably less than 0.15 times the diameter Da of the outer circle Ka. The same applies to the eight ribs 9 'and the grooves 9 "separating them of the lower rotor (secondary rotor) 9, ie the tooth height is also here H not greater than 0.15 times the outer profile diameter Da.
Bei Betrieb des in Figur 1 gezeigten Schraubenkompressors wird seinem Ansaugraum 10, der angrenzend an das in Figur 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 in Figur 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. When the screw compressor shown in FIG. 1 is operating, the suction space 10, which is formed in the rotor housing 1 adjacent to the left end of the profile sections 7, 9 in FIG. 1, is supplied with the gas to be compressed, in particular air, preferably from one or more upstream Compressor stages (not shown) is already precompressed to an intermediate pressure, for example to a pressure in the range from 10 to 15 bar, preferably 12 bar. This precompressed gas is conveyed through the profile sections 7, 9 of the two rotors 3, 5 to the right in FIG. 1 to an outlet (not shown) and is compressed to a final pressure which is preferably in the range from 30 to 50 bar, in particular at about Is 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.

Claims

Ansprüche Expectations
1. Schraubenkompressor mit zwei drehbar gelagerten, gegensinnig antreibbaren Rotoren (3, 5), die über einen Abschnitt ihrer Länge ein Profil (7, 9) mit schaubenförmi- gen Rippen (7, 9') und Nuten aufweisen und mit diesen Rippen und Nuten kämmend und abdichtend ineinandergreifen, dadurch gekennzeichnet, dass die Summe der Anzahlen der schraubenförmigen Rippen (T, 9') der beiden Rotoren mindestens 14 beträgt. 1. Screw compressor with two rotatably mounted rotors (3, 5) which can be driven in opposite directions and which over a section of their length have a profile (7, 9) with screw-shaped ribs (7, 9 ') and grooves and with these ribs and grooves Intermeshing and sealingly interlocking, characterized in that the sum of the numbers of the helical ribs (T, 9 ') of the two rotors is at least 14.
2. 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 (91) aufweist. 2. Screw compressor according to claim 1, wherein one rotor of the main rotor (3) and the other rotor of the secondary rotor (5), characterized in that the profile (7) of the main rotor has six ribs (7 ') and the profile (9) of the Secondary rotor has eight ribs (9 1 ).
3. Schraubenkompressor nach Anspruch 1 oder 2, dadurch gekennzeichnet, dass die Rippenhöhe jedes Rotors (3, 5) nicht größer als das 0,15-fache des Profilaußendurchmessers (Da) des Rotors ist. 3. Screw compressor according to claim 1 or 2, characterized in that the rib height of each rotor (3, 5) is not greater than 0.15 times the outer profile diameter (Da) of the rotor.
4. Schraubenkompressor nach einem der Ansprüche 1 bis 3, wobei jeder Rotor an den Profilabschnitt angrenzende Wellenzapfen (7a, 7b, 9a, 9b) aufweist, dadurch gekennzeichnet, 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. 4. Screw compressor according to one of claims 1 to 3, wherein each rotor has adjacent to the profile section shaft journal (7a, 7b, 9a, 9b), characterized in that the diameter (D, D ') of each shaft journal in the to the profile section ( 7, 9) adjacent area is not less than half the profile outer diameter (Da).
EP06762002A 2005-12-08 2006-06-09 Helical screw compressor Active EP1957798B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102005058698 2005-12-08
PCT/EP2006/005556 WO2007065484A1 (en) 2005-12-08 2006-06-09 Helical screw compressor

Publications (2)

Publication Number Publication Date
EP1957798A1 true EP1957798A1 (en) 2008-08-20
EP1957798B1 EP1957798B1 (en) 2011-02-09

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Application Number Title Priority Date Filing Date
EP06762002A Active EP1957798B1 (en) 2005-12-08 2006-06-09 Helical screw compressor
EP06754262A Withdrawn EP1957799A1 (en) 2005-12-08 2006-06-09 Helical screw compressor
EP06754261.3A Active EP1979618B1 (en) 2005-12-08 2006-06-09 Multi-step helical screw compressor unit
EP06754260.5A Active EP1957797B1 (en) 2005-12-08 2006-06-09 Helical screw compressor comprising a cooling jacket

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EP06754262A Withdrawn EP1957799A1 (en) 2005-12-08 2006-06-09 Helical screw compressor
EP06754261.3A Active EP1979618B1 (en) 2005-12-08 2006-06-09 Multi-step helical screw compressor unit
EP06754260.5A Active EP1957797B1 (en) 2005-12-08 2006-06-09 Helical screw compressor comprising a cooling jacket

Country Status (8)

Country Link
US (4) US7690901B2 (en)
EP (4) EP1957798B1 (en)
CN (2) CN101321955A (en)
AT (1) ATE498071T1 (en)
DE (1) DE502006008894D1 (en)
ES (1) ES2359015T3 (en)
HK (1) HK1127111A1 (en)
WO (4) WO2007065484A1 (en)

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CN101321955A (en) 2008-12-10
EP1979618A1 (en) 2008-10-15
EP1957799A1 (en) 2008-08-20
EP1979618B1 (en) 2016-04-27
EP1957797A1 (en) 2008-08-20
US7690901B2 (en) 2010-04-06
US20080286129A1 (en) 2008-11-20
WO2007065484A1 (en) 2007-06-14
US9091268B2 (en) 2015-07-28
CN101321954B (en) 2012-06-13
ATE498071T1 (en) 2011-02-15
EP1957798B1 (en) 2011-02-09
US20090004036A1 (en) 2009-01-01
WO2007065485A1 (en) 2007-06-14
WO2007065486A1 (en) 2007-06-14
HK1127111A1 (en) 2009-09-18
DE502006008894D1 (en) 2011-03-24
EP1957797B1 (en) 2016-09-28
ES2359015T3 (en) 2011-05-17
US20080286138A1 (en) 2008-11-20
US20130011285A1 (en) 2013-01-10
CN101321954A (en) 2008-12-10
WO2007065487A1 (en) 2007-06-14
US7713039B2 (en) 2010-05-11

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