EP2558726B2 - Compressor flange for screw-type compressor - Google Patents

Compressor flange for screw-type compressor Download PDF

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Publication number
EP2558726B2
EP2558726B2 EP11716393.1A EP11716393A EP2558726B2 EP 2558726 B2 EP2558726 B2 EP 2558726B2 EP 11716393 A EP11716393 A EP 11716393A EP 2558726 B2 EP2558726 B2 EP 2558726B2
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EP
European Patent Office
Prior art keywords
compressor
flange
housing
drive
shaft
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EP11716393.1A
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German (de)
French (fr)
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EP2558726A2 (en
EP2558726B1 (en
Inventor
Engelbert KÖCK
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Knorr Bremse Systeme fuer Schienenfahrzeuge GmbH
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Knorr Bremse Systeme fuer Schienenfahrzeuge GmbH
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • 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
    • F04C18/086—Carter
    • 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
    • F04C29/0042—Driving elements, brakes, couplings, transmissions specially adapted for pumps
    • 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
    • F04C27/00—Sealing arrangements in rotary-piston pumps specially adapted for elastic fluids
    • F04C27/005—Axial sealings for working fluid
    • F04C27/006—Elements specially adapted for sealing of the lateral faces of intermeshing-engagement type pumps, e.g. gear pumps

Definitions

  • the invention relates to a compressor flange for connecting a screw compressor to a drive, having the features of the preamble of claim 1.
  • the invention also relates to a screw compressor having such a compressor flange.
  • Screw compressors currently available have connecting elements for connection to a drive, which are provided with a centering collar or centering pins for centering.
  • the connecting elements regularly include a connecting flange that can be connected to a front cover of the screw compressor.
  • the front cover closes and seals the compressor housing from the outside.
  • a refrigeration compressor with a horizontally flanged electric motor emerges, which in the closed version comprises a flange component for connecting the compressor to the electric motor.
  • the compressor housing has a hub-like projection for receiving the drive shaft and for receiving a centrally arranged projection of the flange component, so that the flange component is centered when it is inserted.
  • a further ring step which is concentric to the central projection, is intended to center the compressor in relation to the electric motor.
  • there is no mechanical shaft seal since a certain amount of leakage is accepted or desired.
  • a hole is provided in the flange component in order to supply lubricant from the electric motor to the interior of the compressor housing.
  • an adapter plate for connecting a compressor to a drive is also known.
  • the adapter plate rests against a shaft bearing and provides a seal that prevents air from entering the compressor through the shaft bearing.
  • the object of the present invention is to provide a compressor flange for connecting a screw compressor to a drive, which requires little manufacturing and assembly effort and combines several functions in one component.
  • the invention is characterized by the features of claim 1.
  • the seals form components of the connecting flange, so that the use of separate sealing means, which have to be installed separately from the flange component, is not necessary.
  • the compressor flange thus simultaneously assumes the function of a front cover, which is usually provided for closing and sealing a screw compressor. This means that the compressor flange also has a closing and sealing function in addition to the connection function. The number of components required can accordingly be reduced, with the result that the manufacturing and assembly costs are also reduced.
  • the axially and radially effective seals can be inserted in grooves on the compressor flange or molded or molded on.
  • the seal against the shaft preferably takes place in the region of the bearing of the shaft, so that the seal is not exposed to any dynamic loading. The seal thus has a long service life.
  • the compressor flange is pot-shaped and, in contact with the compressor housing and the housing of the drive, delimits a cavity for receiving a clutch, which connects the shaft of the compressor to a shaft of the drive.
  • the housing of the clutch by the compressor flange makes it possible to omit a clutch bell and thus use a simple clutch.
  • the number of components can be further reduced.
  • the space requirement is reduced due to the smaller overall size.
  • weight can also be saved.
  • a reduction in the number of components is also associated with reduced assembly costs, since fewer components have to be aligned with one another and fastened to one another. In addition, the places that have to be additionally sealed are reduced. This also reliably avoids the accumulation of manufacturing and/or assembly tolerances.
  • the seals provided on the compressor flange ensure that the clutch accommodated in the cavity of the pot-shaped compressor flange is adequately protected even if a clutch bell housing is omitted. This protection can also be guaranteed if, for example, the screw compressor is used in partially submerged operation. Furthermore, the cavity can serve to accommodate a lubricating medium, since the seals of the compressor flange ensure that no lubricating medium escapes to the outside. If there is a leakage of lubricant in the area of the shaft, the cavity of the cup-shaped compressor flange is used to catch the escaped lubricant.
  • the compressor flange has an axially effective seal for sealing against the housing of the drive. This also ensures a tight connection of the screw compressor to the housing of the drive.
  • annular step is preferably formed on at least one end face of the compressor flange for centering the compressor flange in relation to the compressor housing, the shaft, the bearing and/or the housing of the drive.
  • the compressor flange thus has a centering function at the same time and makes further connection elements, for example in the form of centering pins, superfluous.
  • An annular step for centering with respect to the compressor housing and the drive is preferably formed on each of the two end faces of the compressor flange.
  • an axial projection for the axial position fixing of the bearing is formed on the end face facing the compressor housing.
  • the axial projection can also be designed in such a way that it replaces an annular step arranged on the compressor side for centering.
  • the axial projection can be inserted into a recess formed on the compressor housing or the bearing in such a way that the axial projection is supported not only axially but also radially. In this way, the axial projection on the compressor flange fulfills a holding and centering function.
  • the flange can also have an annular step in the form that it accommodates the lateral surface of the shaft bearing and fixes its axial position. This also enables the flange to be centered on the bearing. The latter can be achieved in that the bearing end protrudes axially beyond the compressor housing or in that the compressor housing has a corresponding recess.
  • the compressor flange can preferably be fastened to the compressor housing by means of screws.
  • bores for receiving the screws are provided in the area of the first ring-shaped contact surface for contacting the compressor flange on the compressor housing.
  • the end face preferably forms the first annular bearing surface for the bearing of the compressor flange on the compressor housing in the region of the bottom of the pot-shaped compressor flange.
  • the cover function of the compressor flange can thus be implemented in a simple manner.
  • the central opening for receiving the shaft is also provided in the area of the bottom of the pot-shaped compressor flange.
  • the end face that radially delimits the cavity and is opposite the bottom of the cup-shaped compressor flange forms the second annular bearing surface for bearing of the compressor flange on the housing of the drive.
  • the compressor flange can also have openings, in particular maintenance and/or venting openings. These are preferably designed in such a way that the sealing function of the compressor flange remains guaranteed.
  • a screw compressor with a compressor flange serving both as a front cover for closing and sealing the compressor housing and as a connecting flange for connecting the compressor housing to the housing of the drive.
  • the space enclosed by the compressor flange can be designed as an open or closed compressor, depending on the requirements of the type of coupling used, the type of shaft connection or other requirements resulting from the application.
  • the only figure shows a section of a screw compressor 2 in the area of the connection to a drive 3 , the connection being effected via a compressor flange 1 .
  • the compressor flange 1 combines several functions in one component, since it not only establishes a connection between the compressor 2 and the drive 3, but at the same time centers the compressor 2 in relation to the drive via annular steps 14, 15 formed on its end faces 16, 17 3 allows.
  • the compressor flange 1 replaces an end cover for closing and sealing the housing 8 of the compressor 2 by an axially effective seal 11 being embedded in a first annular contact surface 7 for contacting the compressor flange 1 with the compressor housing 8 .
  • the compressor flange 1 seals against a shaft 5 of the compressor 2 , which is passed through a central opening 4 of the compressor flange 1 .
  • the radially effective seal 12 is in sealing contact with a bearing 6 which is provided for supporting the shaft 5 of the compressor 2 .
  • the sealing with respect to the shaft 5 of the compressor 2 thus takes place indirectly via the bearing 6. This has the advantage that the radially effective seal 12 is not exposed to any dynamic loading.
  • a further axially effective seal 13 is provided in the end face 17 for sealing the compressor flange 1 with respect to the housing 10 of the drive 3 .
  • the end face 17 also forms a second annular bearing surface 9 for bearing the compressor flange 1 on the housing 10 of the drive 3 .
  • screws 19 are provided, which are passed through bores in the end face 16 for screwing the compressor flange 1 to the compressor housing 8 .
  • the screws 19 ensure that the compressor flange 1 is axially prestressed relative to the compressor housing 8 , with the axially effective seal 11 also being pressed against the compressor housing 8 .
  • the annular step 14 in the area of the end face 16 is designed as an axial extension 18, by means of which the bearing 6 is held in position.
  • the compressor flange 1 thus also fulfills a holding function, with the bearing 6 being held by the connection by means of the screws 19 being ensured.
  • the axial shoulder 18 engages in a form-fitting manner in an annular recess of the compressor housing 8 .
  • the axial projection 18 also centers the compressor flange relative to the compressor housing 8 and/or the shaft 5 of the compressor 2 .
  • an axial receptacle 23 for the axial position fixing of the bearing 6 in the compressor flange can also be formed in the area of the end face 16.
  • the bearing 6 is advantageously designed in such a way that it protrudes in the axial direction, so that it can be at least partially inserted into the axial recess 23 (not shown).
  • the compressor flange 1 of the illustrated embodiment is also pot-shaped, so that a cavity 20 is formed between a base area, which is axially attached to the compressor housing 8, and a side wall area, which in this case is intended to accommodate a clutch 21 for connecting the shaft 5 of the compressor 2 with the shaft 22 of the drive 3 is used.
  • the compressor flange 1 thus also assumes a protective function, which makes the arrangement of a clutch bell unnecessary.
  • the seals 11, 13 ensure that the cavity 20 formed between the compressor 2 and the drive 3 is sealed off from the outside.
  • the compressor flange according to the invention shown in the figure is thus able to combine the functions of a front cover, a flange and a protective hood, while at the same time taking on a centering, holding and sealing function. All of these functions are implemented by a single component, so that the number of components required can be significantly reduced and the manufacturing and assembly costs can be significantly reduced. At the same time, the size and weight of a screw compressor are reduced so that it requires less installation space.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Compressor (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)

Description

Gebiet der Erfindungfield of invention

Die Erfindung betrifft ein Verdichterflansch zur Verbindung eines Schraubenverdichters mit einem Antrieb mit den Merkmalen des Oberbegriffs des Anspruchs 1. Ferner betrifft die Erfindung einen Schraubenverdichter mit einem solchen Verdichterflansch.The invention relates to a compressor flange for connecting a screw compressor to a drive, having the features of the preamble of claim 1. The invention also relates to a screw compressor having such a compressor flange.

Derzeit verfügbare Schraubenkompressoren weisen zur Verbindung mit einem Antrieb Verbindungselemente auf, die zur Zentrierung mit einem Zentrierbund oder Zentrierstiften versehen sind. Die Verbindungselemente umfassen regelmäßig einen Verbindungsflansch, der mit einem Stirndeckel des Schraubenkompressors verbindbar ist. Der Stirndeckel schließt und dichtet das Verdichtergehäuse nach außen ab. Es sind somit regelmäßig mehrere Bauteile erforderlich, die zur Verbindung des Schraubenkompressors mit einem Antrieb entsprechend positioniert und befestigt werden müssen. Der Fertigungs- und Montageaufwand ist somit sehr hoch.Screw compressors currently available have connecting elements for connection to a drive, which are provided with a centering collar or centering pins for centering. The connecting elements regularly include a connecting flange that can be connected to a front cover of the screw compressor. The front cover closes and seals the compressor housing from the outside. Thus, several components are regularly required, which must be positioned and fastened accordingly to connect the screw compressor to a drive. The manufacturing and assembly costs are therefore very high.

Stand der TechnikState of the art

Aus der Auslegeschrift DE 10 44 122 A geht ein Kälteverdichter mit waagerecht angeflanschtem Elektromotor hervor, der in der geschlossenen Ausführung ein Flanschbauteil zur Verbindung des Verdichters mit dem Elektromotor umfasst. Das Verdichtergehäuse weist einen nabenartigen Ansatz zur Aufnahme der Antriebswelle und zur Aufnahme eines zentrisch angeordneten Ansatzes des Flanschbauteils auf, so dass bei Einsetzen des Flanschbauteils eine Zentrierung desselben erfolgt. Durch eine weitere zum zentrischen Ansatz konzentrisch ausgebildete Ringstufe soll eine Zentrierung des Verdichters in Bezug auf den Elektromotor erfolgen. Auf eine Gleitringwellenabdichtung wird vorliegend verzichtet, da eine gewisse Leckage hingenommen wird bzw. erwünscht ist. Des Weiteren ist eine Bohrung im Flanschbauteil vorgesehen, um Schmiermittel aus dem Elektromotor dem Innern des Verdichtergehäuses zuzuführen.From the exposition DE 10 44 122 A a refrigeration compressor with a horizontally flanged electric motor emerges, which in the closed version comprises a flange component for connecting the compressor to the electric motor. The compressor housing has a hub-like projection for receiving the drive shaft and for receiving a centrally arranged projection of the flange component, so that the flange component is centered when it is inserted. A further ring step, which is concentric to the central projection, is intended to center the compressor in relation to the electric motor. In the present case, there is no mechanical shaft seal, since a certain amount of leakage is accepted or desired. Furthermore, a hole is provided in the flange component in order to supply lubricant from the electric motor to the interior of the compressor housing.

Aus der WO 2004/053311 A1 ist ferner eine Adapterplatte zur Verbindung eines Verdichters mit einem Antrieb bekannt. Die Adapterplatte liegt an einem Wellenlager an und stellt eine Adichtung dar, die verhindert, dass über das Wellenlager Luft in den Verdichter gelangt.From the WO 2004/053311 A1 an adapter plate for connecting a compressor to a drive is also known. The adapter plate rests against a shaft bearing and provides a seal that prevents air from entering the compressor through the shaft bearing.

Aus den Druckschriften US 2005/0123415 A1 , DE 7 927 054 U1 und EP 0 048 095 A1 sind darüber hinaus weitere Flanschbauteile bekannt, die eine Verbindung eines Verdichters mit einem Antrieb ermöglichen.From the pamphlets U.S. 2005/0123415 A1 , DE 7 927 054 U1 and EP 0 048 095 A1 In addition, further flange components are known which enable a compressor to be connected to a drive.

Aufgabe der vorliegenden Erfindung ist es, einen Verdichterflansch zur Verbindung eines Schraubenverdichters mit einem Antrieb bereitzustellen, der einen geringen Fertigungs- und Montageaufwand erfordert und mehrere Funktionen in einem Bauteil vereint.The object of the present invention is to provide a compressor flange for connecting a screw compressor to a drive, which requires little manufacturing and assembly effort and combines several functions in one component.

Die Aufgabe wird gelöst durch einen Verdichterflansch mit den Merkmalen des Anspruchs 1. Vorteilhafte Weiterbildungen der Erfindung werden in den auf Anspruch 1 direkt oder indirekt rückbezogenen Unteransprüchenangegeben. Des Weiteren wird ein Schraubenverdichter mit einem solchen Verdichterflansch zur Lösung der Aufgabe vorgeschlagen.The object is achieved by a compressor flange having the features of claim 1. Advantageous developments of the invention are specified in the dependent claims which refer back to claim 1 directly or indirectly. Furthermore, a screw compressor with such a compressor flange is proposed to solve the problem.

Die Erfindung wird gekennzeichnet durch die Merkmale von Anspruch 1. Die Dichtungen bilden Bestandteile des Verbindungsflansches aus, so dass der Einsatz separater Dichtmittel, die getrennt vom Flanschbauteil montiert werden müssen, nicht erforderlich ist. Der Verdichterflansch übernimmt somit gleichzeitig die Funktion eines Stirndeckels, der üblicherweise zum Verschließen und Abdichten eines Schraubenverdichters vorgesehen ist. D.h., der Verdichterflansch übernimmt neben der Verbindungsfunktion auch eine Verschluss- und eine Abdichtungsfunktion. Die Anzahl der erforderlichen Bauteile kann demnach reduziert werden, so dass folglich auch der Fertigungs- und der Montageaufwand verringert werden.The invention is characterized by the features of claim 1. The seals form components of the connecting flange, so that the use of separate sealing means, which have to be installed separately from the flange component, is not necessary. The compressor flange thus simultaneously assumes the function of a front cover, which is usually provided for closing and sealing a screw compressor. This means that the compressor flange also has a closing and sealing function in addition to the connection function. The number of components required can accordingly be reduced, with the result that the manufacturing and assembly costs are also reduced.

Die axial und radial wirksamen Dichtungen können in Nuten am Verdichterflansch eingesetzt oder angespritzt bzw. angeformt sein. Vorzugsweise erfolgt die Abdichtung gegenüber der Welle im Bereich des Lagers der Welle, so dass die Dichtung keiner dynamischen Belastung ausgesetzt ist. Die Dichtung weist somit eine hohe Lebensdauer auf.The axially and radially effective seals can be inserted in grooves on the compressor flange or molded or molded on. The seal against the shaft preferably takes place in the region of the bearing of the shaft, so that the seal is not exposed to any dynamic loading. The seal thus has a long service life.

Erfindungsgemäß ist der Verdichterflansch topfförmig ausgebildet und begrenzt in Anlage am Verdichtergehäuse und am Gehäuse des Antriebs einen Hohlraum zur Aufnahme einer Kupplung, welche die Welle des Verdichters mit einer Welle des Antriebs verbindet. Die Einhausung der Kupplung durch den Verdichterflansch ermöglicht den Wegfall einer Kupplungsglocke und damit den Einsatz einer einfachen Kupplung. Somit kann die Anzahl der Bauteil weiter reduziert werden. Ferner verringert sich der Platzbedarf, aufgrund der geringeren Gesamtbaugröße. Schließlich kann auch Gewicht eingespart werden.According to the invention, the compressor flange is pot-shaped and, in contact with the compressor housing and the housing of the drive, delimits a cavity for receiving a clutch, which connects the shaft of the compressor to a shaft of the drive. The housing of the clutch by the compressor flange makes it possible to omit a clutch bell and thus use a simple clutch. Thus, the number of components can be further reduced. Furthermore, the space requirement is reduced due to the smaller overall size. Finally, weight can also be saved.

Mit einer Reduzierung der Anzahl der Bauteile geht ferner ein reduzierter Montageaufwand einher, da weniger Bauteile zueinander ausgerichtet und miteinander befestigt werden müssen. Zudem reduzieren sich die Stellen, die zusätzlich abgedichtet werden müssen. Auch eine Aufsummierung von Fertigungs-und/oder Montagetoleranzen wird hierdurch sicher vermieden.A reduction in the number of components is also associated with reduced assembly costs, since fewer components have to be aligned with one another and fastened to one another. In addition, the places that have to be additionally sealed are reduced. This also reliably avoids the accumulation of manufacturing and/or assembly tolerances.

Die am Verdichterflansch vorgesehenen Dichtungen gewährleisten auch bei Wegfall einer Kupplungsglocke, dass die im Hohlraum des topfförmigen Verdichterflansches aufgenommene Kupplung ausreichend geschützt ist. Dieser Schutz kann auch gewährleistet werden, wenn beispielsweise der Einsatz des Schraubenverdichters in teilweise eingetauchtem Betrieb erfolgt. Des Weiteren kann der Hohlraum zur Aufnahme eines Schmiermediums dienen, da über die Dichtungen des Verdichterflansches sichergestellt ist, dass kein Schmiermedium nach außen gelangt. Sofern im Bereich der Welle eine Schmiermittelleckage auftreten sollte, dient der Hohlraum des topfförmigen Verdichterflansches dem Auffangen des ausgetretenen Schmiermittels.The seals provided on the compressor flange ensure that the clutch accommodated in the cavity of the pot-shaped compressor flange is adequately protected even if a clutch bell housing is omitted. This protection can also be guaranteed if, for example, the screw compressor is used in partially submerged operation. Furthermore, the cavity can serve to accommodate a lubricating medium, since the seals of the compressor flange ensure that no lubricating medium escapes to the outside. If there is a leakage of lubricant in the area of the shaft, the cavity of the cup-shaped compressor flange is used to catch the escaped lubricant.

Erfindungsgemäß ist vorgesehen, dass der Verdichterflansch eine axial wirksame Dichtung zur Abdichtung gegenüber dem Gehäuse des Antriebs besitzt. Somit ist auch ein dichter Anschluss des Schraubenverdichters am Gehäuse des Antriebs gewährleistet.According to the invention, it is provided that the compressor flange has an axially effective seal for sealing against the housing of the drive. This also ensures a tight connection of the screw compressor to the housing of the drive.

Des Weiteren bevorzugt ist eine Ringstufe an wenigstens einer StirnflächedesVerdichterflanscheszur Zentrierung des Verdichterflansches in Bezug auf das Verdichtergehäuse, die Welle, das Lager und/oder das Gehäuse des Antriebs ausgebildet. Somitweistder Verdichterflansch zugleich eine Zentrierfunktion auf und macht weitere Verbindungselemente, beispielsweise in Form von Zentrierstiften, entbehrlich. Vorzugsweise ist an beiden Stirnflächen des Verdichterflansches jeweils eine Ringstufe zur Zentrierung gegenüber dem Verdichtergehäuse und dem Antrieb ausgebildet.Furthermore, an annular step is preferably formed on at least one end face of the compressor flange for centering the compressor flange in relation to the compressor housing, the shaft, the bearing and/or the housing of the drive. The compressor flange thus has a centering function at the same time and makes further connection elements, for example in the form of centering pins, superfluous. An annular step for centering with respect to the compressor housing and the drive is preferably formed on each of the two end faces of the compressor flange.

Vorteilhafterweise ist an der dem Verdichtergehäuse zugewandten Stirnfläche ein axialer Ansatz zur axialen Lagefixierung des Lagers ausgebildet. D.h., dass nach Verbindung des Verdichterflansches mit dem Verdichtergehäuse der axiale Ansatz an einer radial verlaufenden Fläche des Lagers abgestützt ist. Der axiale Ansatz kann ferner derart ausgebildet sein, dass er eine verdichterseitig angeordnete Ringstufe zur Zentrierung ersetzt. Hierzu ist der axiale Ansatz vorzugsweise derart in eine am Verdichtergehäuse oder dem Lager ausgebildete Ausnehmung einsetzbar, das der axiale Ansatz nicht nur axial, sondern auch radial abgestützt ist. Der axiale Ansatz am Verdichterflansch erfüllt auf diese Weise eine Halte- und eine Zentrierfunktion.Advantageously, an axial projection for the axial position fixing of the bearing is formed on the end face facing the compressor housing. This means that after the compressor flange has been connected to the compressor housing, the axial projection is supported on a radially extending surface of the bearing. The axial projection can also be designed in such a way that it replaces an annular step arranged on the compressor side for centering. For this purpose, the axial projection can be inserted into a recess formed on the compressor housing or the bearing in such a way that the axial projection is supported not only axially but also radially. In this way, the axial projection on the compressor flange fulfills a holding and centering function.

Alternativ kann auch der Flansch eine Ringstufe in der Form aufweisen, dass diese die Mantelfläche des Wellenlagers aufnimmt und dessen axiale Position fixiert. Hierdurch wird auch eine Zentrierung des Flansches am Lager erreicht. Letzteres kann dadurch erreicht werden, dass das Lagerende axial über das Verdichtergehäuse herausragt oder dadurch, dass das Verdichtergehäuse eine entsprechende Ausnehmung aufweist.Alternatively, the flange can also have an annular step in the form that it accommodates the lateral surface of the shaft bearing and fixes its axial position. This also enables the flange to be centered on the bearing. The latter can be achieved in that the bearing end protrudes axially beyond the compressor housing or in that the compressor housing has a corresponding recess.

Der Verdichterflansch ist vorzugsweise mittels Schrauben am Verdichtergehäuse befestigbar. Hierzu sind im Bereich der ersten ringförmigen Anlagefläche zur Anlage des Verdichterflansches am Verdichtergehäuse Bohrungen zur Aufnahme der Schrauben vorgesehen.The compressor flange can preferably be fastened to the compressor housing by means of screws. For this purpose, bores for receiving the screws are provided in the area of the first ring-shaped contact surface for contacting the compressor flange on the compressor housing.

Vorzugsweise bildet die Stirnfläche im Bereich des Bodens des topfförmigen Verdichterflansches die erste ringförmige Anlagefläche zur Anlage des Verdichterflansches am Verdichtergehäuse aus. Somit kann in einfacher Weise die Deckelfunktion des Verdichterflansches realisiert werden. Die zentrale Öffnung zur Aufnahme der Welle ist ebenfalls im Bereich des Bodens des topfförmigen Verdichterflansches vorgesehen. Weiterhin vorzugsweise bildet die den Hohlraum radial begrenzende und dem Boden des topfförmigen Verdichterflansches gegenüberliegende Stirnfläche die zweite ringförmige Anlagefläche zur Anlage des Verdichterflansches am Gehäuse des Antriebs aus.The end face preferably forms the first annular bearing surface for the bearing of the compressor flange on the compressor housing in the region of the bottom of the pot-shaped compressor flange. The cover function of the compressor flange can thus be implemented in a simple manner. The central opening for receiving the shaft is also provided in the area of the bottom of the pot-shaped compressor flange. Furthermore, preferably, the end face that radially delimits the cavity and is opposite the bottom of the cup-shaped compressor flange forms the second annular bearing surface for bearing of the compressor flange on the housing of the drive.

Zur Wartung und/oder zur Entlüftung des Schraubenverdichters kann der Verdichterflansch ferner Öffnungen, insbesondere Wartungs- und/oder Entlüftungsöffnungen, besitzen. Diese sind vorzugsweise derart ausgebildet, dass die Dichtfunktion des Verdichterflansches gewährleistet bleibt.For maintenance and/or venting of the screw compressor, the compressor flange can also have openings, in particular maintenance and/or venting openings. These are preferably designed in such a way that the sealing function of the compressor flange remains guaranteed.

Zur Lösung der Aufgabe wird ferner ein Schraubenverdichter mit einem erfindungsgemäßen Verdichterflansch vorgeschlagen, wobei der Verdichterflansch zugleich als Stirndeckel zum Verschließen und Abdichten des Verdichtergehäuses und als Verbindungsflansch zur Verbindung des Verdichtergehäuses mit dem Gehäuse des Antriebes dient. Dabei kann der vom Verdichterflansch umschlossene Raum - in Abhängigkeit von den Anforderungen der verwendeten Kupplungsart, der Art der Wellenverbindung oder weiteren sich aus der Anwendung ergebenden Anforderungen - als offener oder geschlossener Verdichter ausgeführt sein.To solve the problem, a screw compressor with a compressor flange according to the invention is also proposed, the compressor flange serving both as a front cover for closing and sealing the compressor housing and as a connecting flange for connecting the compressor housing to the housing of the drive. The space enclosed by the compressor flange can be designed as an open or closed compressor, depending on the requirements of the type of coupling used, the type of shaft connection or other requirements resulting from the application.

Eine bevorzugte Ausführungsform der Erfindung wird nachfolgend anhand der einzigen Figur näher erläutert. Diese zeigt einen erfindungsgemäßen Verdichtungsflansch in Anlage an einen Verdichtergehäuse und einem Gehäuse eines Antriebs.A preferred embodiment of the invention is explained in more detail below with reference to the single figure. This shows a compression flange according to the invention in contact with a compressor housing and a housing of a drive.

Ausführliche Beschreibung der ZeichnungDetailed description of the drawing

Die einzige Figur zeigt den Ausschnitt eines Schraubenverdichters 2 im Bereich des Anschlusses an einen Antrieb 3, wobei der Anschluss über einen Verdichterflansch 1 bewirkt wird. Der Verdichterflansch 1 vereint mehrere Funktionen in einem Bauteil, da er nicht nur eine Verbindung zwischen dem Verdichter 2 und dem Antrieb 3 herstellt, sondern über an seinen Stirnflächen 16, 17 ausgebildete Ringstufen 14, 15 gleichzeitig eine Zentrierung des Verdichters 2 in Bezug auf den Antrieb 3 ermöglicht. Zugleich ersetzt der Verdichterflansch 1 einen Stirndeckel zum Verschließen und Abdichten des Gehäuses 8 des Verdichters 2, indem in einer ersten ringförmigen Anlagefläche 7 zur Anlage des Verdichterflansches 1 am Verdichtergehäuse 8 eine axial wirksame Dichtung 11 eingelassen ist. Des Weiteren dichtet der Verdichterflansch 1 gegenüber einer Welle 5 des Verdichters 2 ab, welche durch eine zentrale Öffnung 4 des Verdichterflansches 1 hindurchgeführt ist. Hierzu ist im Bereich der zentralen Öffnung 4 eine radial wirksame Dichtung 12 im Verdichterflansch 1 eingelassen. Die radial wirksame Dichtung 12 liegt dichtend an einem Lager 6 an, das zur Lagerung der Welle 5 des Verdichters 2 vorgesehen ist. Die Abdichtung gegenüber der Welle 5 des Verdichters 2 erfolgt somit mittelbar über das Lager 6. Dies hat den Vorteil, dass die radial wirksame Dichtung 12 keiner dynamischen Belastung ausgesetzt ist.The only figure shows a section of a screw compressor 2 in the area of the connection to a drive 3 , the connection being effected via a compressor flange 1 . The compressor flange 1 combines several functions in one component, since it not only establishes a connection between the compressor 2 and the drive 3, but at the same time centers the compressor 2 in relation to the drive via annular steps 14, 15 formed on its end faces 16, 17 3 allows. At the same time, the compressor flange 1 replaces an end cover for closing and sealing the housing 8 of the compressor 2 by an axially effective seal 11 being embedded in a first annular contact surface 7 for contacting the compressor flange 1 with the compressor housing 8 . Furthermore, the compressor flange 1 seals against a shaft 5 of the compressor 2 , which is passed through a central opening 4 of the compressor flange 1 . For this purpose, in the area of the central opening 4, a radially effective Gasket 12 embedded in compressor flange 1. The radially effective seal 12 is in sealing contact with a bearing 6 which is provided for supporting the shaft 5 of the compressor 2 . The sealing with respect to the shaft 5 of the compressor 2 thus takes place indirectly via the bearing 6. This has the advantage that the radially effective seal 12 is not exposed to any dynamic loading.

Eine weitere axial wirksame Dichtung 13 ist in der Stirnfläche 17 zur Abdichtung des Verdichterflansches 1 gegenüber dem Gehäuse 10 des Antriebs 3 vorgesehen. Die Stirnfläche 17 bildet zudem eine zweite ringförmige Anlagefläche 9 zur Anlage des Verdichterflansches 1 am Gehäuse 10 des Antriebs 3 aus. Zur Fixierung des Verdichterflansches 1 am Verdichtergehäuse 8 sind Schrauben 19 vorgesehen, die durch Bohrungen in der Stirnfläche 16 zur Verschraubung des Verdichterflansches 1 mit dem Verdichtergehäuse 8 geführt werden. Die Schrauben 19 gewährleisten eine axiale Vorspannung des Verdichterflansches 1 gegenüber dem Verdichtergehäuse 8, wobei auch die axial wirksame Dichtung 11 an das Verdichtergehäuse 8 gedrückt wird.A further axially effective seal 13 is provided in the end face 17 for sealing the compressor flange 1 with respect to the housing 10 of the drive 3 . The end face 17 also forms a second annular bearing surface 9 for bearing the compressor flange 1 on the housing 10 of the drive 3 . To fix the compressor flange 1 to the compressor housing 8 , screws 19 are provided, which are passed through bores in the end face 16 for screwing the compressor flange 1 to the compressor housing 8 . The screws 19 ensure that the compressor flange 1 is axially prestressed relative to the compressor housing 8 , with the axially effective seal 11 also being pressed against the compressor housing 8 .

Die Ringstufe 14 im Bereich der Stirnfläche 16 ist bei der dargestellten Ausführungsform als axialer Ansatz 18 ausgebildet, mittels derer das Lager 6 in Position gehalten wird. Somit erfüllt der Verdichterflansch 1 ferner eine Haltefunktion, wobei das Halten des Lagers 6 durch die Verbindung mittels der Schrauben 19 gewährleistet wird. Der axiale Ansatz 18 greift hierzu formschlüssig in eine ringförmige Ausnehmung des Verdichtergehäuses 8 ein. Somit ist gleichzeitig über den axialen Ansatz 18 auch eine Zentrierung des Verdichterflansches gegenüber dem Verdichtergehäuse 8 und/oder der Welle 5 des Verdichters 2 gegeben.In the illustrated embodiment, the annular step 14 in the area of the end face 16 is designed as an axial extension 18, by means of which the bearing 6 is held in position. The compressor flange 1 thus also fulfills a holding function, with the bearing 6 being held by the connection by means of the screws 19 being ensured. For this purpose, the axial shoulder 18 engages in a form-fitting manner in an annular recess of the compressor housing 8 . Thus, at the same time, the axial projection 18 also centers the compressor flange relative to the compressor housing 8 and/or the shaft 5 of the compressor 2 .

Alternativ oder ergänzend zum axialen Ansatz 18 kann im Bereich der Stirnfläche 16 zudem eine axiale Aufnahme 23 zur axialen Lagefixierung des Lagers 6 im Verdichterflansch ausgebildet sein. Vorteilhafterweise ist hierzu das Lager 6 derart ausgebildet, dass es in axialer Richtung vorsteht, so dass es in die axiale Ausnehmung 23 zumindest teilweise einsetzbar ist (nicht dargestellt).As an alternative or in addition to the axial extension 18, an axial receptacle 23 for the axial position fixing of the bearing 6 in the compressor flange can also be formed in the area of the end face 16. For this purpose, the bearing 6 is advantageously designed in such a way that it protrudes in the axial direction, so that it can be at least partially inserted into the axial recess 23 (not shown).

Der Verdichterflansch 1 der dargestellten Ausführungsform ist ferner topfförmig ausgebildet, so dass zwischen einem Bodenbereich, der axial an dem Verdichtergehäuse 8 angeschlagen ist und einem Seitenwandbereich ein Hohlraum 20 ausgebildet wird, der vorliegend der Aufnahme einer Kupplung 21 zur Verbindung der Welle 5 des Verdichters 2 mit der Welle 22 des Antriebs 3 dient. Der Verdichterflansch 1 übernimmt somit auch eine Schutzfunktion, welche die Anordnung einer Kupplungsglocke entbehrlich macht. Die Dichtungen 11, 13 stellen dabei sicher, dass der zwischen dem Verdichter 2 und dem Antrieb 3 ausgebildete Hohlraum 20 nach außen abgedichtet ist.The compressor flange 1 of the illustrated embodiment is also pot-shaped, so that a cavity 20 is formed between a base area, which is axially attached to the compressor housing 8, and a side wall area, which in this case is intended to accommodate a clutch 21 for connecting the shaft 5 of the compressor 2 with the shaft 22 of the drive 3 is used. The compressor flange 1 thus also assumes a protective function, which makes the arrangement of a clutch bell unnecessary. The seals 11, 13 ensure that the cavity 20 formed between the compressor 2 and the drive 3 is sealed off from the outside.

Der in der Figur dargestellte erfindungsgemäße Verdichterflansch vermag somit die Funktionen eines Stirndeckels, eines Flansches und einer Schutzhaube in sich zu vereinen, wobei er gleichzeitig eine Zentrier-, Halte- und Dichtungsfunktion übernimmt. Alle diese Funktionen werden durch ein einziges Bauteil verwirklicht, so dass die Anzahl erforderlicher Bauteile deutlich reduziert werden und der Fertigungs- und Montageaufwand deutlich verringert werden kann. Zugleich werden Baugröße und Gewicht eines Schraubenverdichters reduziert, so dass dieser weniger Bauraum erfordert.The compressor flange according to the invention shown in the figure is thus able to combine the functions of a front cover, a flange and a protective hood, while at the same time taking on a centering, holding and sealing function. All of these functions are implemented by a single component, so that the number of components required can be significantly reduced and the manufacturing and assembly costs can be significantly reduced. At the same time, the size and weight of a screw compressor are reduced so that it requires less installation space.

BezugszeichenlisteReference List

11
Verdichterflanschcompressor flange
22
Verdichtercompressor
33
Antriebdrive
44
zentrale Öffnungcentral opening
55
Welle des Verdichtersshaft of the compressor
66
Lagercamp
77
erste ringförmige Anlageflächefirst annular bearing surface
88th
Gehäuse des Verdichtershousing of the compressor
99
zweite ringförmige Anlageflächesecond annular bearing surface
1010
Gehäuse des Antriebshousing of the drive
1111
axial wirksame Dichtungaxially effective seal
1212
radial wirksame Dichtungradially effective seal
1313
axial wirksame Dichtungaxially effective seal
1414
Ringstufering level
1515
Ringstufering level
1616
Stirnflächeface
1717
Stirnflächeface
1818
axialer Ansatzaxial approach
1919
Schraubenscrews
2020
Hohlraumcavity
2121
Kupplungcoupling
2222
Welle des Antriebsdrive shaft
2323
AufnahmeRecording

Claims (7)

  1. Compressor flange (1) for connecting a screw-type compressor (2) to a drive (3), the compressor flange (1) having a central orifice (4) for the reception of a shaft (5) and of a bearing (6), and possessing a first ring-shaped bearing surface (7) for bearing against a housing (8) of the compressor (2) and a second ring-shaped bearing surface (9) for bearing against a housing (10) of the drive (3), wherein the compressor flange (1) comprises, furthermore, axially and radially active seals (11, 12) for sealing off with respect to the compressor housing (8) and to the shaft (5), so that an open compressor housing (8) can be closed and sealed off, using the compressor flange (1), characterized in that the compressor flange (1) is of pot-shaped design and, when bearing against the compressor housing (8) and against the housing (10) of the drive (3), delimits a cavity (20) for receiving a clutch (21) which connects the shaft (5) of the compressor (2) to a shaft (22) of the drive (3), wherein the compressor flange (1) possesses, furthermore, an axially active seal (13) for sealing off with respect to the housing (10) of the drive (3), and the axial seals (11, 13) and the compressor flange (1) are designed in such a way that the cavity (20) formed between the compressor (2) and the drive (3) is sealed off outwardly.
  2. Compressor flange according to Claim 1, characterized in that an annular step (14, 15) is formed on at least one end face (16, 17) of the compressor flange (1) for the purpose of centering the compressor flange (1) with respect to the compressor housing (8), to the shaft (5) and/or to the housing (10) of the drive (3).
  3. Compressor flange according to one of the preceding claims, characterized in that an axial extension (18) for fixing the axial position of the bearing (6) is formed on the end face (16) facing the compressor housing (8).
  4. Compressor flange according to one of the preceding claims, characterized in that an axial receptacle (23) for fixing the axial position of the bearing (6) is formed on the end face (16) facing the compressor housing (8).
  5. Compressor flange according to one of the preceding claims, characterized in that the compressor flange (1) can be fastened to the compressor housing (8) by means of screws (19).
  6. Compressor flange according to one of the preceding claims, characterized in that the end face (16) forms, in the region of the bottom of the pot-shaped compressor flange (1), the first ring-shaped bearing surface (7), and the end face (17) radially delimiting the cavity (20) and lying opposite the bottom forms the second ring-shaped bearing surface (8) .
  7. Screw-type compressor having a compressor flange (1) according to one of the preceding claims, the compressor flange (1) serving at the same time as an end cover for closing and sealing off the compressor housing (8) and as a connecting flange for connecting the compressor housing (8) to the housing (10) of the drive (3).
EP11716393.1A 2010-04-16 2011-04-13 Compressor flange for screw-type compressor Active EP2558726B2 (en)

Applications Claiming Priority (2)

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DE102010015151A DE102010015151A1 (en) 2010-04-16 2010-04-16 Compressor flange for screw compressors
PCT/EP2011/055754 WO2011128349A2 (en) 2010-04-16 2011-04-13 Compressor flange for screw-type compressor

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EP2558726A2 EP2558726A2 (en) 2013-02-20
EP2558726B1 EP2558726B1 (en) 2017-10-18
EP2558726B2 true EP2558726B2 (en) 2023-03-29

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US (1) US9523363B2 (en)
EP (1) EP2558726B2 (en)
JP (1) JP5868387B2 (en)
CN (1) CN103154520B (en)
BR (1) BR112012026459B1 (en)
CA (1) CA2796626C (en)
DE (1) DE102010015151A1 (en)
MX (1) MX342998B (en)
RU (1) RU2561515C2 (en)
WO (1) WO2011128349A2 (en)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102010015151A1 (en) 2010-04-16 2011-10-20 Knorr-Bremse Systeme für Schienenfahrzeuge GmbH Compressor flange for screw compressors
DE102016011503A1 (en) 2016-09-21 2018-03-22 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH System for a commercial vehicle comprising a screw compressor and an electric motor
DE102016011442A1 (en) 2016-09-21 2018-03-22 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH System for a commercial vehicle comprising a screw compressor and an electric motor
DE102016011504A1 (en) 2016-09-21 2018-03-22 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH System for a commercial vehicle comprising a screw compressor and an electric motor
CN106451843A (en) * 2016-10-27 2017-02-22 驰美电机（上海）有限公司 Special bearingless direct-connection sealing permanent-magnet synchronous motor with graphene winding for compressor
US20220145880A1 (en) * 2020-11-11 2022-05-12 Server Products, Inc. Flexible impeller pump for flowable food product

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH456832A (en) † 1966-11-04 1968-05-31 Wissenschaftl Techn Zentrum Wt Drive and bearing arrangement for screw compressors
DE2434404A1 (en) † 1973-07-20 1975-02-06 Svenska Rotor Maskiner Ab PARALLEL AND EXTERNAL ROTARY PISTON COMPRESSORS WITH COMBING
DE19716549C2 (en) † 1997-04-19 2000-02-10 Compair Drucklufttechnik Gmbh Screw compressors for stationary or mobile compressors

Family Cites Families (19)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE456832C (en) 1924-08-05 1928-03-02 Fikentscher Fa F Surface planer
AT196893B (en) 1956-07-07 1958-03-25 Raimund Culk Refrigeration compressor with horizontally flanged electric motor
US3209990A (en) 1962-01-18 1965-10-05 Atlas Copco Ab Two stage screw rotor machines
AR207639A1 (en) 1973-12-26 1976-10-22 Pfizer A PROCEDURE FOR PREPARING PIRIDO (3,2-D) 1,3-DIOXIN-6-EPOXYETHANS AND INTERMEDIARY COMPOUNDS UNPROVED OF THERAPEUTIC ACTIVITY
DE7927054U1 (en) * 1979-09-24 1981-10-15 Isartaler Schraubenkompressoren GmbH, 8192 Geretsried COMPRESSOR SYSTEM
DE3161646D1 (en) 1980-09-05 1984-01-19 British Nuclear Fuels Plc Pump for heavy gases
DE3149245A1 (en) 1981-12-11 1983-06-16 Isartaler Schraubenkompressoren GmbH, 8192 Geretsried "COMPRESSOR SYSTEM"
DE58907244D1 (en) * 1989-07-20 1994-04-21 Leybold Ag Friction pump with bell-shaped rotor.
SE506513C2 (en) 1995-10-23 1997-12-22 Lysholm Techn Ab Transmission with a two-piece connector
DE19728434C2 (en) * 1997-07-03 1999-07-29 Busch Sa Atel Screw compressors for compressible media
JP2000170680A (en) 1998-09-30 2000-06-20 Aisin Seiki Co Ltd Vacuum pump
ITBO20000668A1 (en) 2000-11-17 2002-05-17 Fini Elettrocostruzioni Meccan SCREW COMPRESSOR
AU2003265299A1 (en) * 2002-12-10 2004-06-30 Ingersoll-Rand Energy Systems Corporation Hermetic motor and gas booster
JP2004301054A (en) * 2003-03-31 2004-10-28 Toyota Industries Corp Hybrid compressor
JP2005163713A (en) 2003-12-04 2005-06-23 Toyota Industries Corp Fluid compressor
JP2005188326A (en) 2003-12-24 2005-07-14 Toyota Industries Corp Fluid compressor
EP1944273A1 (en) 2007-01-15 2008-07-16 Rockwool International A/S Process and apparatus for making mineral fibers
CN101624984B (en) 2009-08-05 2011-07-13 徐道敏 Vertical single screw air compressor
DE102010015151A1 (en) 2010-04-16 2011-10-20 Knorr-Bremse Systeme für Schienenfahrzeuge GmbH Compressor flange for screw compressors

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH456832A (en) † 1966-11-04 1968-05-31 Wissenschaftl Techn Zentrum Wt Drive and bearing arrangement for screw compressors
DE2434404A1 (en) † 1973-07-20 1975-02-06 Svenska Rotor Maskiner Ab PARALLEL AND EXTERNAL ROTARY PISTON COMPRESSORS WITH COMBING
DE19716549C2 (en) † 1997-04-19 2000-02-10 Compair Drucklufttechnik Gmbh Screw compressors for stationary or mobile compressors

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
Offenkundige Vorbenutzung einer BOGE-Schraubenkompressoranlage †

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MX2012011978A (en) 2012-12-17
CN103154520A (en) 2013-06-12
CA2796626C (en) 2018-06-26
BR112012026459A2 (en) 2016-08-09
CN103154520B (en) 2016-03-16
RU2561515C2 (en) 2015-08-27
EP2558726A2 (en) 2013-02-20
US9523363B2 (en) 2016-12-20
EP2558726B1 (en) 2017-10-18
US20130064694A1 (en) 2013-03-14
WO2011128349A2 (en) 2011-10-20
RU2012148731A (en) 2014-05-27
JP2013534582A (en) 2013-09-05
DE102010015151A1 (en) 2011-10-20
BR112012026459B1 (en) 2021-01-26
MX342998B (en) 2016-10-21
CA2796626A1 (en) 2011-10-20
JP5868387B2 (en) 2016-02-24
WO2011128349A3 (en) 2013-05-02

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