EP0644317A1 - Liquid ring pump - Google Patents

Liquid ring pump Download PDF

Info

Publication number
EP0644317A1
EP0644317A1 EP94106156A EP94106156A EP0644317A1 EP 0644317 A1 EP0644317 A1 EP 0644317A1 EP 94106156 A EP94106156 A EP 94106156A EP 94106156 A EP94106156 A EP 94106156A EP 0644317 A1 EP0644317 A1 EP 0644317A1
Authority
EP
European Patent Office
Prior art keywords
housing
impeller
work space
liquid ring
space housing
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
EP94106156A
Other languages
German (de)
French (fr)
Other versions
EP0644317B1 (en
Inventor
Klaus Dipl.-Ing. Domagalla
Udo Dipl.-Ing. Segebrecht
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.)
Sihi GmbH and Co KG
Original Assignee
Sihi GmbH and Co KG
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 Sihi GmbH and Co KG filed Critical Sihi GmbH and Co KG
Priority to CA002131081A priority Critical patent/CA2131081C/en
Priority to AU71625/94A priority patent/AU673761B2/en
Priority to CZ19942184A priority patent/CZ291259B6/en
Priority to US08/304,534 priority patent/US5509789A/en
Priority to JP21706994A priority patent/JP3538234B2/en
Priority to MYPI94002450A priority patent/MY111315A/en
Priority to CN94115333A priority patent/CN1035837C/en
Priority to SK1119-94A priority patent/SK281523B6/en
Priority to TW083109028A priority patent/TW257826B/zh
Publication of EP0644317A1 publication Critical patent/EP0644317A1/en
Application granted granted Critical
Publication of EP0644317B1 publication Critical patent/EP0644317B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/10—Outer members for co-operation with rotary pistons; Casings
    • F01C21/104—Stators; Members defining the outer boundaries of the working chamber
    • 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
    • F04C19/00—Rotary-piston pumps with fluid ring or the like, specially adapted for elastic fluids

Definitions

  • the invention relates to a liquid ring gas pump according to the preamble of claim 1.
  • the pump comprises a connection housing flanged to the drive motor, which forms the suction and pressure connections, a cup-shaped work space housing which has a flange for connection to a flange of the Has connection housing, and a control disc arranged between these two housings. All parts of the housing are strongly dimensioned castings. This is common in liquid ring gas pumps because the efficiency is largely dependent on the maintenance of little play between the impeller and the work space housing and this play should not be affected by housing deformation. This is also the reason why the cheaper sheet metal construction, which has long been used in other types of pumps, has not yet found its way into liquid ring gas pumps.
  • the invention has for its object to achieve a more economical production of liquid ring gas pumps without loss of quality.
  • the solution according to the invention consists in the features of claim 1 and preferably the subclaims. It consists mainly in the fact that the work area housing is designed as a pot-shaped, deep-drawn, connection-free sheet metal part.
  • the impeller which forms open cells between the vanes towards the control disk, is largely closed on the side facing away from the control disk by an end disk or a radial expansion of the hub; the overflow paths are therefore longer on this side than on the side cooperating with the control disk, so that greater play can be tolerated.
  • an axial thrust acts on the impeller in the direction of the control disc, so that an approximately increased bearing clearance does not increase the critical gap between the impeller and the control disc, but at most the less critical clearance between the end face of the impeller that is remote from the control disc and the bottom of the working area housing.
  • the medium connections are provided in the connection housing, so that the work area housing cannot be warped due to warping during manufacture or due to the introduction of force during use. This also applies to the drain opening and the operating fluid supply.
  • the work space housing has a substantially radial connecting flange for connection to the connection housing, which is formed in one piece with the rest of the work space housing.
  • This poses the problem that, due to the manufacturing process, a rounding arises at the transition from the cylindrical part of the housing to the flange which forms a peripheral gap adjacent to the control disk.
  • efforts are made to allow the smallest possible distance at the apex of the housing, where the outer edges of the impeller come closest to the circumference of the housing, in order to keep the overflow losses that arise from the overflow of liquid from one cell to the next cell of lower pressure .
  • the gap formed in the rounding of the sheet metal housing represents an additional overflow cross section.
  • the invention has recognized that this effort is unnecessary if the size of the gap does not exceed a certain cross-sectional area. More specifically, it is coming mainly on the area of the gap which is closer to the impeller and which has a larger width than the part of the gap which is further out.
  • the cross-sectional area of the gap as such is therefore less meaningful than the size of the incircle that can be inscribed in the gap cross-sectional area, as stated in claims 3 and 4.
  • This incircle diameter should not exceed 1.5 times, preferably 0.85 times the wall thickness of the work area housing. In general, it should not be larger than 3.5%, preferably 2.5% of the impeller diameter in pumps with a conventional impeller diameter (for example 125 to 210 mm diameter, speed 3000 rpm).
  • Dirt particles that get into the liquid ring and have a higher density than the liquid are caught in the liquid ring and circle around its outer circumference. It is known to provide a dirt removal opening in the control disk on the outer circumference of the liquid ring, through which part of the liquid with the particles can leave the liquid ring.
  • the dirt particles preferably collect in the gap between the rounding of the working space housing and the control disk. It is therefore expedient if the dirt discharge opening is arranged at this gap, i.e. at least adjacent to these, but preferably completely or partially radially outside the inner diameter of the cylindrical part of the work space housing.
  • connection housing 3 is connected via the flange 2, which contains the suction and pressure chamber of the pump and the suction and pressure ports leading to the outside.
  • control disk 4 which contains the suction and pressure openings (not shown), and then the work space housing 5 with the connecting flange 6 and the housing wall 7 remote from the drive.
  • the connecting flange 6 is connected to the connection housing 3 by means of the screws 17 and the control disk 4.
  • the control disk 4 is fastened to the connection housing 3 by means of additional screws 8.
  • the centering of the flange 6, like the centering of the control disk 4 with respect to the connection housing 3, can take place in that the bore in the flange 6 and the control disk 4 are designed with correspondingly narrow tolerances for two of the screws 17.
  • the impeller 13 rotates with vanes 14, which is fastened on the shaft end 15 and can be adjusted in the longitudinal direction by means of the screw 16, in order to maintain the intended play with respect to the control disk 4 and the housing wall 7 remote from the motor.
  • the shaft is mounted in a longitudinally fixed manner in the bearing 18 of the motor 1 near the pump. It is not recommended to close the motor 1 bearing away from the pump as a fixed bearing use, because otherwise thermal expansion of the motor shaft can affect the position of the impeller.
  • the mechanical seal the spring of which is supported on the impeller 13, is provided within the connection housing 3.
  • the deep-drawing process used for the production of the work area housing 5 requires that the housing edges at 9 and 11 turn out to be rounded. This can be taken into account in that the outer wing corner 10 is rounded or beveled accordingly. However, an embodiment is preferred in which the rounding of the housing corner 9 is turned out as far as is required by the impeller diameter in the course of the plan machining of the housing wall 10.
  • the vanes of the impeller can have a radial projection in the manner shown at 12.
  • this projection can be dispensed with practically without loss of efficiency if the radius 20 of the rounding 11 is made small enough so that the area of the gap 21 between the rounding 11, the control disk 4 and the line 22, which the cylindrical part of the housing 5 parallel to the outer edges of the wings 14 (ie approximately axially parallel) continues, is small enough. Since it is mainly the parts of this surface that are closer to the axis that are important in this context, the size of the inscribed circle 23 inscribed on this surface is chosen as the dimension, the diameter of which should not exceed the values specified above.
  • the original sheet metal thickness of the working space housing 5 is preferably approximately 4 mm with an impeller diameter of 125 mm and preferably approximately 6 mm with an impeller diameter of 210 mm.
  • a bore 24 is arranged in the control disc 4, which leads into a special space 25 of the connection housing. It is arranged in such a way that it is at least adjacent to line 22, but better - as shown in FIG. 2 - is at least partially radially outside of this line. Dirt particles that collect in the gap 21, together with part of the liquid, can leave the working space through the bore 24 and enter the space 25, in which they can be deposited or from which they can also be removed from time to time.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Rotary Pumps (AREA)
  • Gyroscopes (AREA)
  • Fluid-Pressure Circuits (AREA)

Abstract

Single-stage liquid-ring gas pump that can be flanged to a drive unit. The inlet and discharge connections are provided on a connection housing (3) which is intended for connection to the drive unit. Provided on that side of the connection housing which is remote from the drive are a control plate (4) and a working-space housing (5) with an impeller (14) revolving therein. The said impeller interacts in a sealing manner on its open side with the control plate and on its largely closed side (19) with an end wall (7) of the working-space housing (5). The working-space housing is designed as a deep-drawn sheet-metal part and has no medium connections. For connection with the connection housing or the control plate, it is provided with a radial connecting flange (6). The transition from the cylindrical part to the connecting flange (6) of the working-space housing (5) is rounded in such a way on the inside that the gap remaining between this rounding and the control plate remains below a certain size. Its incircle should not be larger than 3.5% of the impeller diameter. <IMAGE>

Description

Die Erfindung bezieht sich auf eine Flüssigkeitsringgaspumpe nach dem Oberbegriff des Anspruchs 1.The invention relates to a liquid ring gas pump according to the preamble of claim 1.

Bei einer bekannten Pumpe dieser Art (Prospekt Hick Hargreaves: "CHR Series Liquid Ring Pumps") umfaßt die Pumpe ein an den Antriebsmotor angeflanschtes Anschlußgehäuse, welches die Saug- und Druckanschlüsse bildet, ein topfförmiges Arbeitsraumgehäuse, das einen Flansch zur Verbindung mit einem Flansch des Anschlußgehäuses aufweist, und eine zwischen diesen beiden Gehäusen angeordnete Steuerscheibe. Sämtliche Gehäuseteile sind kräftig dimensionierte Gußstücke. Dies ist bei Flüssigkeitsringgaspumpen deshalb üblich, weil der Wirkungsgrad weitgehend von der Einhaltung geringen Spiels zwischen dem Flügelrad und dem Arbeitsraumgehäuse abhängig ist und dieses Spiel nicht durch Gehäuseverformung beeinträchtigt werden soll. Dies ist auch Grund dafür, daß die billigere Blechbauweise, die bei anderen Pumpentypen seit langem angewendet wird, bei Flüssigkeitsringgaspumpen noch nicht Eingang gefunden hat.In a known pump of this type (Hick Hargreaves brochure: "CHR Series Liquid Ring Pumps"), the pump comprises a connection housing flanged to the drive motor, which forms the suction and pressure connections, a cup-shaped work space housing which has a flange for connection to a flange of the Has connection housing, and a control disc arranged between these two housings. All parts of the housing are strongly dimensioned castings. This is common in liquid ring gas pumps because the efficiency is largely dependent on the maintenance of little play between the impeller and the work space housing and this play should not be affected by housing deformation. This is also the reason why the cheaper sheet metal construction, which has long been used in other types of pumps, has not yet found its way into liquid ring gas pumps.

Der Erfindung liegt die Aufgabe zugrunde, eine wirtschaftlichere Fertigung von Flüssigkeitsringgaspumpen ohne Qualitätsverlust zu erreichen. Die erfindungsgemäße Lösung besteht in den Merkmalen des Anspruchs 1 und vorzugsweise der Unteransprüche. Sie besteht hauptsächlich darin, daß das Arbeitsraumgehäuse als topfförmig tiefgezogenes, anschlußfreies Blechteil ausgeführt wird.The invention has for its object to achieve a more economical production of liquid ring gas pumps without loss of quality. The solution according to the invention consists in the features of claim 1 and preferably the subclaims. It consists mainly in the fact that the work area housing is designed as a pot-shaped, deep-drawn, connection-free sheet metal part.

Beim Zustandekommen der Erfindung war das Vorurteil zu überwinden, daß vergleichsweise dünnwandige Blechbauteile nicht in der Lage sind, die engen Toleranzen bezüglich des Spiels am Flügelrad zu gewährleisten. Diese sind zwischen den Stirnseiten des Flügelrads und den damit zusammenwirkenden Gehäuseteilen, nämlich Steuerscheibe einerseits und Stirnwand des Arbeitsraumgehäuses andererseits, erforderlich, damit nicht die Überströmung von den unter höherem Druck stehenden Flügelzellen zu den unter niedrigerem Druck befindlichen Zellen zu Wirkungsgradverlusten führt.When the invention came about, the prejudice had to be overcome that comparatively thin-walled sheet metal components are not able to guarantee the tight tolerances with regard to the play on the impeller. These are required between the end faces of the impeller and the housing parts interacting with it, namely the control disk on the one hand and the end wall of the work area housing on the other, so that the overflow from the vane cells under higher pressure to the cells under lower pressure leads to efficiency losses.

In der Tat muß man bei vergleichsweise dünnwandiger Ausführung des Bodens des Arbeitsraumgehäuses in Blechbauweise mit stärkeren Verformungen rechnen als bei einem entsprechenden Gußkörper. Jedoch hat die Erfindung erkannt, daß dies aus zwei Gründen vernachlässigbar ist. Zum einen ist das Flügelrad, das zur Steuerscheibe hin offene Zellen zwischen den Flügeln bildet, auf der der Steuerscheibe abgewandten Seite durch eine stirnseitige Scheibe oder eine radiale Erweiterung der Nabe weitgehend geschlossen; die Überströmwege sind daher auf dieser Seite länger als auf der mit der Steuerscheibe zusammenwirkenden Seite, so daß größeres Spiel geduldet werden kann. Zum anderen wirkt auf das Flügelrad ein Axialschub in Richtung zur Steuerscheibe hin, so daß ein etwa vergrößertes Lagerspiel die kritische Spaltweite zwischen dem Flügelrad und der Steuerscheibe nicht vergrößert, sondern höchstens das weniger kritische Spiel zwischen der steuerscheibenfernen Stirnseite des Flügelrads und dem Boden des Arbeitsraumgehäuses. Die Mediumsanschlüsse sind im Anschlußgehäuse vorgesehen, damit das Arbeitsraumgehäuse nicht durch Verzug bei der Herstellung oder durch Krafteinleitung im Gebrauch verzogen werden kann. Das gilt auch für die Entleerungsöffnung und die Betriebsflüssigkeitszufuhr.In fact, with comparatively thin-walled design of the bottom of the work space housing in sheet metal construction, greater deformations must be expected than with a corresponding cast body. However, the invention has recognized that this is negligible for two reasons. On the one hand, the impeller, which forms open cells between the vanes towards the control disk, is largely closed on the side facing away from the control disk by an end disk or a radial expansion of the hub; the overflow paths are therefore longer on this side than on the side cooperating with the control disk, so that greater play can be tolerated. On the other hand, an axial thrust acts on the impeller in the direction of the control disc, so that an approximately increased bearing clearance does not increase the critical gap between the impeller and the control disc, but at most the less critical clearance between the end face of the impeller that is remote from the control disc and the bottom of the working area housing. The medium connections are provided in the connection housing, so that the work area housing cannot be warped due to warping during manufacture or due to the introduction of force during use. This also applies to the drain opening and the operating fluid supply.

Zwar ist es bei einem Seitenkanalgebläse bekannt, das Gehäuse, das das Flügelrad einschließt, teilweise als tiefgezogenes Blechteil auszubilden (DE-B 23 31 614); jedoch konnte die Erfindung dadurch nicht nahegelegt werden, weil das Gehäuse bei der bekannten Pumpe nicht mit dem Flügelrad zur Bildung eines Arbeitsraums zusammenwirkt und daher auch kein enges Spiel mit diesem bilden muß. Der Fachmann konnte dadurch nur erfahren, was er ohnehin wußte, daß nämlich die Blechbauweise zu einer Verminderung der Gehäusekosten führen kann. Er erfuhr nicht, wie er die speziellen Schwierigkeiten, die sich der Nutzung der Blechbauweise bei Flüssigkeitsringgaspumpen entgegenstellen, überwinden konnte.In the case of a side channel blower, it is known to partially design the housing, which includes the impeller, as a deep-drawn sheet metal part (DE-B 23 31 614); however, the invention could not be suggested because the housing in the known pump does not cooperate with the impeller to form a working space and therefore does not have to form a narrow game with it. The specialist could only find out what he knew anyway, namely that sheet metal construction can lead to a reduction in housing costs. He did not learn how to overcome the special difficulties of using sheet metal construction with liquid ring gas pumps.

Vorteilhafterweise weist das Arbeitsraumgehäuse einen im wesentlichen radialen Verbindungsflansch zum Anschluß an das Anschlußgehäuse auf, der einstückig mit dem übrigen Arbeitsraumgehäuse ausgebildet ist. Dies wirft das Problem auf, daß herstellungsbedingt am Übergang vom zylindrischen Teil des Gehäuses zum Flansch eine Abrundung entsteht, die benachbart der Steuerscheibe einen Umfangsspalt bildet. Man ist aber bemüht, am sog. Scheitel des Gehäuses, wo die Außenkanten des Flügelrads dem Gehäuseumfang am nächsten kommen, einen möglichst geringen Abstand zuzulassen, um die Überströmverluste gering zu halten, die durch Überströmen von Flüssigkeit von einer Zelle zur nächsten Zelle niedrigeren Drucks entstehen. Der bei der Abrundung des Blechgehäuses gebildete Spalt stellt einen zusätzlichen Überströmquerschnitt dar. Dem kann man dadurch abhelfen, daß man die Außenkanten des Flügelrads an dieser Stelle mit einem Vorsprung versieht, der in den Spalt hineinragt. Jedoch hat die Erfindung erkannt, daß dieser Aufwand unnötig ist, sofern die Größe des Spalts eine gewisse Querschnittsfläche nicht übersteigt. Genauer gesagt, kommt es hauptsächlich auf denjenigen Bereich des Spalts an, der dem Flügelrad nähergelegen ist und der eine größere Weite als der weiter außen liegende Teil des Spalts besitzt. Die Querschnittsfläche des Spalts als solche ist daher weniger aussagekräftig als die Größe des Inkreises, der der Spaltquerschnittsfläche einbeschrieben werden kann, wie es in Anspruch 3 und 4 angegeben ist. Dieser Inkreisdurchmesser soll die 1,5-fache, vorzugsweise die 0,85-fache Wanddicke des Arbeitsraumgehäuses nicht überschreiten. Er soll bei Pumpen üblichen Flügelraddurchmessers (beispielsweise 125 bis 210 mm Durchmesser, Drehzahl 3000 min⁻¹) - allgemeiner gesprochen - nicht größer sein als 3,5%, vorzugsweise 2,5% des Flügelraddurchmessers.Advantageously, the work space housing has a substantially radial connecting flange for connection to the connection housing, which is formed in one piece with the rest of the work space housing. This poses the problem that, due to the manufacturing process, a rounding arises at the transition from the cylindrical part of the housing to the flange which forms a peripheral gap adjacent to the control disk. However, efforts are made to allow the smallest possible distance at the apex of the housing, where the outer edges of the impeller come closest to the circumference of the housing, in order to keep the overflow losses that arise from the overflow of liquid from one cell to the next cell of lower pressure . The gap formed in the rounding of the sheet metal housing represents an additional overflow cross section. This can be remedied by providing the outer edges of the impeller with a projection at this point, which protrudes into the gap. However, the invention has recognized that this effort is unnecessary if the size of the gap does not exceed a certain cross-sectional area. More specifically, it is coming mainly on the area of the gap which is closer to the impeller and which has a larger width than the part of the gap which is further out. The cross-sectional area of the gap as such is therefore less meaningful than the size of the incircle that can be inscribed in the gap cross-sectional area, as stated in claims 3 and 4. This incircle diameter should not exceed 1.5 times, preferably 0.85 times the wall thickness of the work area housing. In general, it should not be larger than 3.5%, preferably 2.5% of the impeller diameter in pumps with a conventional impeller diameter (for example 125 to 210 mm diameter, speed 3000 rpm).

Schmutzpartikeln, die in den Flüssigkeitsring geraten und eine höhere Dichte als die Flüssigkeit haben, werden im Flüssigkeitsring gefangen und kreisen an dessen Außenumfang. Es ist bekannt, in der Steuerscheibe eine Schmutzabführungsöffnung am äußeren Umfang des Flüssigkeitsrings vorzusehen, durch die ein Teil der Flüssigkeit mit den Partikeln den Flüssigkeitsring verlassen kann. Die Schmutzpartikeln sammeln sich bevorzugt in dem Spalt zwischen der Abrundung des Arbeitsraumgehäuses und der Steuerscheibe. Es ist daher zweckmäßig, wenn die Schmutzabführungsöffnung an diesem Spalt angeordnet wird, d.h. zumindest angrenzend an diesen, vorzugsweise aber ganz oder teilweise radial außerhalb des Innendurchmessers des zylindrischen Teils des Arbeitsraumgehäuses.Dirt particles that get into the liquid ring and have a higher density than the liquid are caught in the liquid ring and circle around its outer circumference. It is known to provide a dirt removal opening in the control disk on the outer circumference of the liquid ring, through which part of the liquid with the particles can leave the liquid ring. The dirt particles preferably collect in the gap between the rounding of the working space housing and the control disk. It is therefore expedient if the dirt discharge opening is arranged at this gap, i.e. at least adjacent to these, but preferably completely or partially radially outside the inner diameter of the cylindrical part of the work space housing.

Wenn im Zusammenhang der Erfindung von Tiefziehen des Arbeitsraumgehäuses gesprochen wird, so ist damit in erster Linie die Verformung mit starren, axial zueinander bewegten Formwerkzeugen gemeint; jedoch soll der Begriff auch andere, verwandte Umformtechniken einbeziehen, wie das Drücken, das Streckziehen und die Hochgeschwindigkeitsumformung.If in the context of the invention one speaks of deep drawing of the work space housing, this primarily means the deformation with rigid, axially moving molds; however, the term is intended to include other related forming techniques such as pressing, stretching and high speed forming.

Wenn von Dünnwandigkeit des Arbeitsraumgehäuses gesprochen wird, so ist damit die Größenordnung von 3-8 mm, vorzugsweise 4-6 mm gemeint bei einem Flügelraddurchmesser von 125 bis 210 mm Durchmesser. Bei größeren Pumpen wird eine entsprechend größere Dicke verwendet.If one speaks of thin-walledness of the work space housing, then the order of magnitude of 3-8 mm is preferred 4-6 mm meant with an impeller diameter of 125 to 210 mm diameter. A correspondingly larger thickness is used for larger pumps.

Die Erfindung wird im folgenden unter Bezugnahme auf die Zeichnung näher erläutert, die eine vorteilhaftes Ausführungsbeispiel veranschaulicht. Darin zeigen:

Fig.1
einen Längsschnitt durch die Pumpe und
Fig.2
einen vergrößerten Längsschnitt durch den Übergangsbereich am zylindrischen Teil des Arbeitsraumgehäuses zu dessen Flansch.
The invention is explained in more detail below with reference to the drawing, which illustrates an advantageous embodiment. In it show:
Fig. 1
a longitudinal section through the pump and
Fig. 2
an enlarged longitudinal section through the transition region on the cylindrical part of the work space housing to the flange.

An den Motor 1 (oder einem Lagerbock, Spaltrohrantrieb od. dgl.) ist über den Flansch 2 das Anschlußgehäuse 3 angeschlossen, welches den Saug- und Druckraum der Pumpe enthält sowie die nach außen führenden Saug- und Druckstutzen. Es folgt die Steuerscheibe 4, welche die nicht dargestellten Saug- und Drucköffnungen enthält, sowie anschließend das Arbeitsraumgehäuse 5 mit Anschlußflansch 6 und antriebsferner Gehäusewand 7. Der Anschlußflansch 6 ist unter Zwischenschaltung der Steuerscheibe 4 mittels der Schrauben 17 an das Anschlußgehäuse 3 angeschlossen. Die Steuerscheibe 4 ist über zusätzliche Schrauben 8 am Anschlußgehäuse 3 befestigt. Die Zentrierung des Flanschs 6 kann ebenso wie die Zentrierung der Steuerscheibe 4 gegenüber dem Anschlußgehäuse 3 dadurch erfolgen, daß für zwei der Schrauben 17 die Bohrung in dem Flansch 6 und der Steuerscheibe 4 entsprechend eng toleriert ausgeführt sind.To the motor 1 (or a bearing block, canned drive or the like.) The connection housing 3 is connected via the flange 2, which contains the suction and pressure chamber of the pump and the suction and pressure ports leading to the outside. This is followed by the control disk 4, which contains the suction and pressure openings (not shown), and then the work space housing 5 with the connecting flange 6 and the housing wall 7 remote from the drive. The connecting flange 6 is connected to the connection housing 3 by means of the screws 17 and the control disk 4. The control disk 4 is fastened to the connection housing 3 by means of additional screws 8. The centering of the flange 6, like the centering of the control disk 4 with respect to the connection housing 3, can take place in that the bore in the flange 6 and the control disk 4 are designed with correspondingly narrow tolerances for two of the screws 17.

In dem Arbeitsraumgehäuse 5 läuft das Flügelrad 13 mit Flügeln 14 um, das auf dem Wellenende 15 befestigt ist und mittels der Schraube 16 in Längsrichtung einstellbar ist, um das vorgesehene Spiel gegenüber der Steuerscheibe 4 und der motorfernen Gehäusewand 7 einzuhalten. Die Welle ist in dem pumpennahen Lager 18 des Motors 1 längsfest gelagert. Es empfiehlt sich nicht, das pumpenferne Lager des Motors 1 als Festlager zu verwenden, weil andernfalls Wärmedehnungen der Motorwelle die Lage des Flügelrads beeinflussen können.In the working space housing 5, the impeller 13 rotates with vanes 14, which is fastened on the shaft end 15 and can be adjusted in the longitudinal direction by means of the screw 16, in order to maintain the intended play with respect to the control disk 4 and the housing wall 7 remote from the motor. The shaft is mounted in a longitudinally fixed manner in the bearing 18 of the motor 1 near the pump. It is not recommended to close the motor 1 bearing away from the pump as a fixed bearing use, because otherwise thermal expansion of the motor shaft can affect the position of the impeller.

Die Gleitringdichtung, deren Feder sich an dem Flügelrad 13 abstützt, ist innerhalb des Anschlußgehäuses 3 vorgesehen.The mechanical seal, the spring of which is supported on the impeller 13, is provided within the connection housing 3.

Während die Nabe des Flügelrads zur Steuerscheibe 4 hin im Durchmesser abnimmt, um eine leichte Füllung und Entleerung der Flügelradzellen durch die Steueröffnungen der Steuerscheibe 4 hindurch zu ermöglichen, nimmt der Nabendurchmesser zur antriebsfernen Seite hin zu und erweitert sich schließlich zu einer stirnseitigen Scheibe 19, die mit geringem Spiel mit der ebenen Gehäusewand 7 zusammenwirkt. Diese kann (muß aber nicht) ebenso wie die Anschlußfläche des Flanschs 6 plan bearbeitet sein. Dennoch ist damit zu rechnen, daß sie sich unter den unterschiedlichen Drücken im Arbeitsraum ein wenig verformt und daher an dieser Stelle wechselndes und ggf. erhöhtes Spiel auftritt. In demselben Sinne wirkt innerhalb des vom Lager 18 zur Verfügung gestellten Spiels der auf das Laufrad einwirkende Axialschub. Dennoch muß nicht damit gerechnet werden, daß zwischen dem Flügelrad und der Gehäusewand 7 Überströmverluste eintreten, die im Vergleich mit den entsprechenden Verlusten an der anderen Stirnseite des Flügelrads ins Gewicht fallen, weil dank der Flügelradscheibe 19 die Überströmwege länger sind.As the hub of the impeller towards the control disk 4 decreases in diameter in order to allow easy filling and emptying of the impeller cells through the control openings of the control disk 4, the hub diameter increases towards the side remote from the drive and finally widens to an end disk 19, which interacts with little play with the flat housing wall 7. This can (but does not have to) be machined just like the connection surface of the flange 6. Nevertheless, it is to be expected that it will deform a little under the different pressures in the work area and therefore there will be changing and possibly increased play at this point. The axial thrust acting on the impeller acts within the play provided by the bearing 18 in the same sense. Nevertheless, it must not be expected that 7 overflow losses occur between the impeller and the housing wall, which are significant in comparison with the corresponding losses on the other end face of the impeller because, thanks to the impeller disk 19, the overflow paths are longer.

Das für die Herstellung des Arbeitsraumgehäuses 5 verwendete Tiefziehverfahren bedingt, daß die Gehäusekanten bei 9 und 11 gerundet ausfallen. Dem kann man dadurch Rechnung tragen, daß die äußere Flügelecke 10 entsprechend gerundet oder abgeschrägt ausgeführt wird. Bevorzugt wird aber eine Ausführung, bei der die Rundung der Gehäuseecke 9 im Zuge der Planbearbeitung der Gehäusewand 10 so weit ausgedreht wird, wie dies der Flügelraddurchmesser verlangt.The deep-drawing process used for the production of the work area housing 5 requires that the housing edges at 9 and 11 turn out to be rounded. This can be taken into account in that the outer wing corner 10 is rounded or beveled accordingly. However, an embodiment is preferred in which the rounding of the housing corner 9 is turned out as far as is required by the impeller diameter in the course of the plan machining of the housing wall 10.

Um zu vermeiden, daß die steuerscheibenseitige Gehäuserundung 11 einen unerwünscht großen Überströmquerschnitt bildet, können die Flügel des Flügelrads an dieser Stelle in der bei 12 gezeigten Weise einen radialen Vorsprung aufweisen. Jedoch hat sich gezeigt, daß man auf diesen Vorsprung praktisch ohne Wirkungsgradeinbuße verzichten kann, wenn der Radius 20 der Abrundung 11 klein genug gemacht wird, so daß die Fläche des Spalts 21 zwischen der Rundung 11, der Steuerscheibe 4 und der Linie 22, welche den zylindrischen Teil des Gehäuses 5 parallel zu den Außenkanten der Flügel 14 (also etwa achsparallel) fortsetzt, klein genug ist. Da es in diesem Zusammenhang hauptsächlich auf die achsnäheren Teile dieser Fläche ankommt, wird als Maß die Größe des dieser Fläche einbeschriebenen Inkreises 23 gewählt, dessen Durchmesser die weiter oben angegebenen Werte nicht überschreiten soll.In order to avoid that the curve 11 on the control disk side forms an undesirably large overflow cross section, At this point, the vanes of the impeller can have a radial projection in the manner shown at 12. However, it has been shown that this projection can be dispensed with practically without loss of efficiency if the radius 20 of the rounding 11 is made small enough so that the area of the gap 21 between the rounding 11, the control disk 4 and the line 22, which the cylindrical part of the housing 5 parallel to the outer edges of the wings 14 (ie approximately axially parallel) continues, is small enough. Since it is mainly the parts of this surface that are closer to the axis that are important in this context, the size of the inscribed circle 23 inscribed on this surface is chosen as the dimension, the diameter of which should not exceed the values specified above.

Die ursprüngliche Blechdicke des Arbeitsraumgehäuses 5 beträgt bei einem Flügelraddurchmesser von 125 mm vorzugsweise etwa 4 mm und bei einem Flügelraddurchmesser von 210 mm vorzugsweise etwa 6 mm.The original sheet metal thickness of the working space housing 5 is preferably approximately 4 mm with an impeller diameter of 125 mm and preferably approximately 6 mm with an impeller diameter of 210 mm.

Nahe dem Spalt 21 ist in der Steuerscheibe 4 eine Bohrung 24 angeordnet, die in einen besonderen Raum 25 des Anschlußgehäuses führt. Sie ist so angeordnet, daß sie zumindest an die Linie 22 angrenzt, besser aber - wie in Fig. 2 gezeigt - zumindest teilweise sich radial außerhalb dieser Linie befindet. Schmutzpartikeln, die sich bei dem Spalt 21 sammeln, können zusammen mit einem Teil der Flüssigkeit durch die Bohrung 24 den Arbeitsraum verlassen und in den Raum 25 übertreten, in welchem sie sich ablagern können oder von dem sie von Zeit zu Zeit auch abgezogen werden können.Near the gap 21, a bore 24 is arranged in the control disc 4, which leads into a special space 25 of the connection housing. It is arranged in such a way that it is at least adjacent to line 22, but better - as shown in FIG. 2 - is at least partially radially outside of this line. Dirt particles that collect in the gap 21, together with part of the liquid, can leave the working space through the bore 24 and enter the space 25, in which they can be deposited or from which they can also be removed from time to time.

Claims (5)

Einstufige, an einer Antriebseinheit anflanschbare Flüssigkeitsringgaspumpe mit einem die Saug- und Druckanschlüsse bildenden Anschlußgehäuse (3), einer Steuerscheibe (4) zwischen dem Anschlußgehäuse (3), einem Arbeitsraumgehäuse (5) und einem in dem Arbeitsraumgehäuse fliegend gelagert umlaufenden Flügelrad (14), das an seiner offenen Stirnseite mit der Steuerscheibe (4) und an seiner großenteils geschlossenen Stirnseite (19) mit einer Stirnwand (7) des Arbeitsraumgehäuses (5) dichtend zusammenwirkt, wobei das Arbeitsraumgehäuse (5) fern der Antriebseinheit (1) angeordnet ist, dadurch gekennzeichnet, daß das Arbeitsraumgehäuse (5) als tiefgezogenes Blechteil ausgebildet ist und sämtliche Mediumsanschlüsse am Anschlußgehäuse (3) vorgesehen sind.Single-stage liquid ring gas pump that can be flange-mounted on a drive unit, with a connection housing (3) forming the suction and pressure connections, a control disk (4) between the connection housing (3), a work space housing (5) and an impeller (14) that is overhung in the work space housing, which cooperates sealingly on its open end face with the control disk (4) and on its largely closed end face (19) with an end wall (7) of the work area housing (5), the work area housing (5) being arranged remote from the drive unit (1), thereby characterized in that the work space housing (5) is designed as a deep-drawn sheet metal part and all medium connections are provided on the connection housing (3). Flüssigkeitsringgaspumpe nach Anspruch 1, dadurch gekennzeichnet, daß das Arbeitsraumgehäuse (5) einen im wesentlichen radialen Verbindungsflansch (6) aufweist.Liquid ring gas pump according to claim 1, characterized in that the working space housing (5) has an essentially radial connecting flange (6). Flüssigkeitsringgaspumpe nach Anspruch 2, dadurch gekennzeichnet, daß der innenseitige Übergang (11) von dem im wesentlichen zylindrischen Teil des Arbeitsraumgehäuses (5) zu dem Verbindungsflansch (6) abgerundet ist und der Durchmesser des Inkreises (23), der der Längsschnitt-Zwickelfläche (21) zwischen der Abrundung (11), der Steuerscheibe (4) und der zur Flügelradkante parallelen Fluchtverlängerung (22) der Arbeitsraumbegrenzung einbeschreibbar ist, nicht größer ist als die 1,5-fache Wanddicke des Arbeitsraumgehäuses.Liquid ring gas pump according to claim 2, characterized in that the inside transition (11) from the substantially cylindrical part of the work space housing (5) to the connecting flange (6) is rounded and the diameter of the incircle (23) corresponds to that of the longitudinal cut gusset surface (21 ) between the rounding (11), the control disk (4) and the escape extension (22) parallel to the impeller edge of the work space limitation, is not greater than 1.5 times the wall thickness of the work space housing. Flüssigkeitsringgaspumpe nach Anspruch 3, dadurch gekennzeichnet, daß der Durchmesser des Inkreises (23) alternativ nicht größer ist als 3,5% des Flügelraddurchmessers.Liquid ring gas pump according to claim 3, characterized in that the diameter of the inscribed circle (23) is alternatively not greater than 3.5% of the impeller diameter. Flüssigkeitsringgaspumpe nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, daß eine Schmutzabführungsöffnung (24) in der Steuerscheibe (4) derart angeordnet ist, daß sie an den Spalt (21) zwischen der Steuerscheibe (4) und der Abrundung (11) am Übergang vom zylindrischen Teil zum Flansch (6) des Arbeitsraumgehäuses (5) zumindest angrenzt und vorzugsweise ganz oder teilweise radial außerhalb des Innendurchmessers des zylindrischen Teils des Arbeitsraumgehäuses liegt.Liquid ring gas pump according to one of claims 1 to 4, characterized in that a dirt discharge opening (24) is arranged in the control disc (4) in such a way that it contacts the gap (21) between the control disc (4) and the rounding (11) at the transition from the cylindrical part to the flange (6) of the work space housing (5) at least adjacent and preferably completely or partially radially outside the inner diameter of the cylindrical part of the work space housing.
EP94106156A 1993-09-16 1994-04-20 Liquid ring pump Expired - Lifetime EP0644317B1 (en)

Priority Applications (9)

Application Number Priority Date Filing Date Title
CA002131081A CA2131081C (en) 1993-09-16 1994-08-29 Liquid ring gas pump
AU71625/94A AU673761B2 (en) 1993-09-16 1994-08-31 Liquid ring gas pump
CZ19942184A CZ291259B6 (en) 1993-09-16 1994-09-08 Single-stage leyer-ring gas compressor
JP21706994A JP3538234B2 (en) 1993-09-16 1994-09-12 Liquid ring gas pump
US08/304,534 US5509789A (en) 1993-09-16 1994-09-12 Liquid ring pump having a sheet metal working chamber casing
MYPI94002450A MY111315A (en) 1993-09-16 1994-09-14 Liquid ring gas pump.
CN94115333A CN1035837C (en) 1993-09-16 1994-09-15 Liquid ring gas pump
SK1119-94A SK281523B6 (en) 1993-09-16 1994-09-16 Single-stage liquid-ring gas pump
TW083109028A TW257826B (en) 1993-09-16 1994-09-30

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4331489 1993-09-16
DE4331489A DE4331489A1 (en) 1993-09-16 1993-09-16 Liquid ring gas pump in block design

Publications (2)

Publication Number Publication Date
EP0644317A1 true EP0644317A1 (en) 1995-03-22
EP0644317B1 EP0644317B1 (en) 1997-03-05

Family

ID=6497871

Family Applications (1)

Application Number Title Priority Date Filing Date
EP94106156A Expired - Lifetime EP0644317B1 (en) 1993-09-16 1994-04-20 Liquid ring pump

Country Status (7)

Country Link
EP (1) EP0644317B1 (en)
AT (1) ATE149632T1 (en)
DE (2) DE4331489A1 (en)
DK (1) DK0644317T3 (en)
ES (1) ES2101379T3 (en)
GR (1) GR3023681T3 (en)
TW (1) TW257826B (en)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19825521A1 (en) * 1998-06-08 2000-01-27 Siemens Ag Liquid ring pump
DE19911683A1 (en) * 1999-03-09 2000-09-21 Hielscher Gmbh Ultrasonic sonotrode, grips tip resiliently for e.g. welding, cutting or spot welding, avoiding conventional clamping screw which causes losses and overheating
DE19913632A1 (en) * 1999-03-25 2000-10-05 Siemens Ag Liquid ring pump
WO2004109111A1 (en) * 2003-05-26 2004-12-16 Luk Automobiltechnik Gmbh & Co. Kg Vane-cell pump provided with a deep-drawn metal-sheet pot

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2731451B1 (en) * 1977-07-12 1978-04-13 Siemens Ag Liquid ring compressor or vacuum pump
EP0159968A2 (en) * 1984-04-24 1985-10-30 CORINT S.r.l. Pneumatic vane pump with body of stamped sheet-metal
EP0389838A2 (en) * 1989-03-30 1990-10-03 Inoxpa, S.A. Housing for rotary pump

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS4921705A (en) * 1972-06-21 1974-02-26

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2731451B1 (en) * 1977-07-12 1978-04-13 Siemens Ag Liquid ring compressor or vacuum pump
EP0159968A2 (en) * 1984-04-24 1985-10-30 CORINT S.r.l. Pneumatic vane pump with body of stamped sheet-metal
EP0389838A2 (en) * 1989-03-30 1990-10-03 Inoxpa, S.A. Housing for rotary pump

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19825521A1 (en) * 1998-06-08 2000-01-27 Siemens Ag Liquid ring pump
DE19825521C2 (en) * 1998-06-08 2000-05-04 Siemens Ag Liquid ring pump
DE19911683A1 (en) * 1999-03-09 2000-09-21 Hielscher Gmbh Ultrasonic sonotrode, grips tip resiliently for e.g. welding, cutting or spot welding, avoiding conventional clamping screw which causes losses and overheating
DE19913632A1 (en) * 1999-03-25 2000-10-05 Siemens Ag Liquid ring pump
DE19913632C2 (en) * 1999-03-25 2001-02-08 Siemens Ag Liquid ring pump
WO2004109111A1 (en) * 2003-05-26 2004-12-16 Luk Automobiltechnik Gmbh & Co. Kg Vane-cell pump provided with a deep-drawn metal-sheet pot

Also Published As

Publication number Publication date
DK0644317T3 (en) 1997-09-22
ES2101379T3 (en) 1997-07-01
GR3023681T3 (en) 1997-09-30
EP0644317B1 (en) 1997-03-05
DE4331489A1 (en) 1995-03-23
ATE149632T1 (en) 1997-03-15
TW257826B (en) 1995-09-21
DE59401906D1 (en) 1997-04-10

Similar Documents

Publication Publication Date Title
DE3308227C2 (en)
DE69005510T2 (en) Pump to separate gas from a liquid to be pumped.
DE69304770T2 (en) Pump housing in sheet metal construction
DE3601674C2 (en)
EP0237868B1 (en) Radial or axial flow centrifugal pump
DE69206051T2 (en) Motor driven pump system.
EP0645521B1 (en) Liquid ring gas pump
EP0392975A1 (en) Rotary scroll supercharger for compressible media
EP2250376A1 (en) Turbo engine with improved compensating piston gasket
DE6904086U (en) CENTRIFUGAL PUMP WITH HYDRAULIC SEAL ARRANGEMENTS
EP0760907B1 (en) Vane cell pump
EP0644317A1 (en) Liquid ring pump
WO1994019610A1 (en) Liquid ring machine and process for operating it
DE29513904U1 (en) Side channel centrifugal pump with stage packages in sheet metal construction
EP1230486B1 (en) Pump for a fluid or gaseous medium
DE4217259A1 (en) DOUBLE PUMP
EP0692075A1 (en) Sheet-metal-construction pump stage
DE7613173U1 (en) SCREW PUMP
EP1477682B1 (en) Liquid ring gas pump
DE1293388B (en) Rotary piston vacuum pump with oil-sealed housing and vertical arrangement of the rotor and the shaft
DE19913632C2 (en) Liquid ring pump
EP0599204A1 (en) Submersible pump assembly
DE3153102C2 (en) Vane air pump
DE2321043A1 (en) ROTARY LISTON CYLINDER
DE10034195C1 (en) Dredger pump has welded sheet metal pump wheel provided with 2 discs having axially projecting blades

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 DE DK ES FR GB GR IE IT LI LU MC NL PT SE

RBV Designated contracting states (corrected)

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

K1C1 Correction of patent application (title page) published

Effective date: 19950322

17P Request for examination filed

Effective date: 19950920

R17P Request for examination filed (corrected)

Effective date: 19950915

17Q First examination report despatched

Effective date: 19960607

GRAG Despatch of communication of intention to grant

Free format text: ORIGINAL CODE: EPIDOS AGRA

GRAH Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOS IGRA

GRAH Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOS IGRA

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

RIN1 Information on inventor provided before grant (corrected)

Inventor name: SEGEBRECHT, UDO, DIPL.-ING.

Inventor name: DOMAGALLA, KLAUS, DIPL.-ING.

AK Designated contracting states

Kind code of ref document: B1

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

REF Corresponds to:

Ref document number: 149632

Country of ref document: AT

Date of ref document: 19970315

Kind code of ref document: T

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

REF Corresponds to:

Ref document number: 59401906

Country of ref document: DE

Date of ref document: 19970410

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

Free format text: 72390

REG Reference to a national code

Ref country code: CH

Ref legal event code: NV

Representative=s name: TROESCH SCHEIDEGGER WERNER AG

ITF It: translation for a ep patent filed

Owner name: UFFICIO TECNICO ING. A. MANNUCCI

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

Effective date: 19970603

ET Fr: translation filed
REG Reference to a national code

Ref country code: ES

Ref legal event code: FG2A

Ref document number: 2101379

Country of ref document: ES

Kind code of ref document: T3

REG Reference to a national code

Ref country code: GR

Ref legal event code: FG4A

Free format text: 3023681

REG Reference to a national code

Ref country code: DK

Ref legal event code: T3

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
REG Reference to a national code

Ref country code: GB

Ref legal event code: IF02

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

Ref country code: MC

Payment date: 20090422

Year of fee payment: 16

Ref country code: IE

Payment date: 20090430

Year of fee payment: 16

Ref country code: ES

Payment date: 20090424

Year of fee payment: 16

Ref country code: DK

Payment date: 20090423

Year of fee payment: 16

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

Ref country code: SE

Payment date: 20090427

Year of fee payment: 16

Ref country code: PT

Payment date: 20090413

Year of fee payment: 16

Ref country code: NL

Payment date: 20090427

Year of fee payment: 16

Ref country code: LU

Payment date: 20090428

Year of fee payment: 16

Ref country code: IT

Payment date: 20090427

Year of fee payment: 16

Ref country code: FR

Payment date: 20090420

Year of fee payment: 16

Ref country code: AT

Payment date: 20090423

Year of fee payment: 16

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

Ref country code: BE

Payment date: 20090429

Year of fee payment: 16

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

Ref country code: CH

Payment date: 20090427

Year of fee payment: 16

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

Ref country code: GR

Payment date: 20090428

Year of fee payment: 16

Ref country code: GB

Payment date: 20090424

Year of fee payment: 16

BERE Be: lapsed

Owner name: *SIHI G.M.B.H. & CO. K.G.

Effective date: 20100430

REG Reference to a national code

Ref country code: NL

Ref legal event code: V1

Effective date: 20101101

EUG Se: european patent has lapsed
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: 20100430

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

REG Reference to a national code

Ref country code: DK

Ref legal event code: EBP

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

Effective date: 20100420

REG Reference to a national code

Ref country code: IE

Ref legal event code: MM4A

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20101230

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: 20101101

Ref country code: IE

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

Effective date: 20100420

Ref country code: AT

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

Effective date: 20100420

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: 20101020

Ref country code: LI

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

Effective date: 20100430

Ref country code: CH

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

Effective date: 20100430

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: 20100420

Ref country code: BE

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

Effective date: 20100430

Ref country code: GR

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

Effective date: 20101103

Ref country code: IT

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

Effective date: 20100420

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: 20100503

REG Reference to a national code

Ref country code: ES

Ref legal event code: FD2A

Effective date: 20110715

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: 20110705

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: 20100421

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

Ref country code: FR

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

Effective date: 20100430

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

Ref country code: DE

Payment date: 20120625

Year of fee payment: 19

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: 20100421

Ref country code: LU

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

Effective date: 20100420

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

Ref country code: DE

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

Effective date: 20131101

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 59401906

Country of ref document: DE

Effective date: 20131101