EP0955466A1 - Annular gap seal - Google Patents
Annular gap seal Download PDFInfo
- Publication number
- EP0955466A1 EP0955466A1 EP98106690A EP98106690A EP0955466A1 EP 0955466 A1 EP0955466 A1 EP 0955466A1 EP 98106690 A EP98106690 A EP 98106690A EP 98106690 A EP98106690 A EP 98106690A EP 0955466 A1 EP0955466 A1 EP 0955466A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- pressure
- machine according
- sealing
- stage
- seal
- 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
Links
- 238000007789 sealing Methods 0.000 claims abstract description 29
- 239000000463 material Substances 0.000 claims abstract description 4
- 239000007788 liquid Substances 0.000 claims description 12
- 239000007791 liquid phase Substances 0.000 claims description 4
- 238000000034 method Methods 0.000 claims description 3
- 238000011144 upstream manufacturing Methods 0.000 claims description 3
- 238000009434 installation Methods 0.000 claims description 2
- 239000012071 phase Substances 0.000 claims description 2
- 239000012528 membrane Substances 0.000 claims 1
- 239000012530 fluid Substances 0.000 abstract 1
- 238000010276 construction Methods 0.000 description 2
- 229910052751 metal Inorganic materials 0.000 description 2
- 239000002184 metal Substances 0.000 description 2
- 150000002739 metals Chemical class 0.000 description 2
- 239000007787 solid Substances 0.000 description 2
- UONOETXJSWQNOL-UHFFFAOYSA-N tungsten carbide Chemical compound [W+]#[C-] UONOETXJSWQNOL-UHFFFAOYSA-N 0.000 description 2
- VYZAMTAEIAYCRO-UHFFFAOYSA-N Chromium Chemical compound [Cr] VYZAMTAEIAYCRO-UHFFFAOYSA-N 0.000 description 1
- WGLPBDUCMAPZCE-UHFFFAOYSA-N Trioxochromium Chemical compound O=[Cr](=O)=O WGLPBDUCMAPZCE-UHFFFAOYSA-N 0.000 description 1
- 230000005540 biological transmission Effects 0.000 description 1
- 239000000919 ceramic Substances 0.000 description 1
- 229910000423 chromium oxide Inorganic materials 0.000 description 1
- 239000011248 coating agent Substances 0.000 description 1
- 238000000576 coating method Methods 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- -1 hard chrome plating Chemical class 0.000 description 1
- 230000001050 lubricating effect Effects 0.000 description 1
- 238000005461 lubrication Methods 0.000 description 1
- 238000012423 maintenance Methods 0.000 description 1
- 239000000203 mixture Substances 0.000 description 1
- TWNQGVIAIRXVLR-UHFFFAOYSA-N oxo(oxoalumanyloxy)alumane Chemical compound O=[Al]O[Al]=O TWNQGVIAIRXVLR-UHFFFAOYSA-N 0.000 description 1
- RVTZCBVAJQQJTK-UHFFFAOYSA-N oxygen(2-);zirconium(4+) Chemical compound [O-2].[O-2].[Zr+4] RVTZCBVAJQQJTK-UHFFFAOYSA-N 0.000 description 1
- 239000002245 particle Substances 0.000 description 1
- 238000007747 plating Methods 0.000 description 1
- 229910010271 silicon carbide Inorganic materials 0.000 description 1
- HBMJWWWQQXIZIP-UHFFFAOYSA-N silicon carbide Chemical compound [Si+]#[C-] HBMJWWWQQXIZIP-UHFFFAOYSA-N 0.000 description 1
- 238000009736 wetting Methods 0.000 description 1
- 229910001928 zirconium oxide Inorganic materials 0.000 description 1
Images
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
- F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
- F04C15/0003—Sealing arrangements in rotary-piston machines or pumps
- F04C15/0034—Sealing arrangements in rotary-piston machines or pumps for other than the working fluid, i.e. the sealing arrangements are not between working chambers of the machine
- F04C15/0038—Shaft sealings specially adapted for rotary-piston machines or pumps
Definitions
- the invention relates to a fluid-carrying machine, in particular a pump, with a component rotating in a stationary housing part within an annular gap, the stationary housing part separating an interior having a higher product pressure from an exterior having a lower pressure, in which the rotating component is mounted in an external bearing , which is sealed from the interior by a sealing system.
- the invention relates to a screw pump with at least one feed screw, which is enclosed by a housing which has at least one suction port and at least one pressure port, the suction port being connected to a suction space upstream of the feed screw and the pressure port being connected to a pressure space downstream of the feed screw, of the devices for separating the respective liquid phase from the gas phase of the medium stream emerging from the feed screw and has a lower section for receiving at least a portion of the separated liquid phase, a liquid short-circuit line being connected to this lower pressure chamber section communicates with the suction chamber and, together with the conveying elements, forms a closed circuit for a quantity of liquid required for permanent sealing.
- a liquid short-circuit line being connected to this lower pressure chamber section communicates with the suction chamber and, together with the conveying elements, forms a closed circuit for a quantity of liquid required for permanent sealing.
- the invention has for its object to develop a machine of the type described above with an improved sealing system for the rotating component.
- this object is achieved according to the invention in that the annular gap is formed between two extremely hard, wear-resistant materials slide bearing shells, which form a first pressure reduction stage according to the principle of action of a radial slide bearing, the one in the axial direction Leakage from this first sealing stage in the conveying process of the turbomachine returning device is connected downstream, which is followed by a second sealing stage in the axial direction, which is designed as a simple seal in the form of a lip seal and / or a simple mechanical seal.
- a two-stage sealing system is thus provided.
- the first stage is used to reduce pressure and uses the principle of action of a radial plain bearing with the construction of a hydrodynamic wedge.
- the plain bearing shells can be made from solid industrial ceramics (e.g. based on aluminum oxide or zirconium oxide), from solid hard metals (e.g. based on silicon carbide or tungsten carbide) or from coated metals (e.g. hard chrome plating, tungsten carbide or chromium oxide coating).
- the structure of this first sealing stage has the advantage that, on the one hand, an effective hydrodynamic lubricating wedge is built up from the liquid in the pumped medium, but, on the other hand, any particles that have penetrated into the annular gap are simply ground between them due to the extreme hardness and wear resistance of the plain bearing shells.
- the feedback of the leakage of the first sealing stage can e.g. B. by suitable pressure drop between the outlet and inlet side of the machine (with the outlet-side arrangement of the seal) or z. B. by external tools such. B. a pump (with inlet-side arrangement of the seal).
- the second sealing stage provided according to the invention minimizes the leakage at the lowest differential pressures in order to protect the environment or mechanical functional elements.
- the second sealing stage can be designed as a simple sealing system in the form of a lip sealing ring or a single-acting mechanical seal.
- the second Seal stage can also be designed as a multiple circuit of sealing systems of conventional design z. B. as a lip seal with a downstream mechanical seal or as a V-ring with a downstream lip seal and a downstream mechanical seal.
- Figure 1 shows a previously known (see DE 43 16 735 C2) screw pump, which has two contactless intermeshing, opposing pairs of conveying screws as conveying elements, each comprising a right-handed screw 1 and a left-handed screw 2.
- the interlocking conveyor screws together with the housing surrounding them, form 3 individually closed delivery chambers.
- the torque is transmitted from the drive shaft to the driven shaft by means of a gear transmission 4 arranged outside the pump housing 3.
- the pump housing 3 has a suction nozzle 5 and a pressure nozzle 6.
- the medium 9 flowing to the pump through the suction nozzle 5 is supplied in the pump housing 3 in two partial flows to the respective central suction chamber 10, that of the associated delivery screw 1 or 2 is connected upstream. Downstream of these feed screws is a pressure chamber 11, which is closed axially outwards by a shaft seal 12, which is used to seal an outer bearing 13.
- a liquid short-circuit line 14 is connected, which is connected to the suction chamber 10.
- the partial liquid volume flow separated on the pressure side from the conveyed liquid-gas mixture and metered back into the suction area is identified by arrow 15 and is conveyed again as a liquid circulation from the suction chamber 10 into the pressure chamber 11.
- the liquid level in the pump housing 3 or pressure chamber 11 can generally be below the shafts 7, 8.
- the wetting of the shaft seals 12 as a result of the direct inflow is generally sufficient for sufficient lubrication of these shaft seals 12.
- FIG. 1 shows an embodiment of the invention.
- a component rotates within an annular gap 17, which is the shaft 8 of FIG. 1.
- the stationary housing part 16 separates an interior having a higher product pressure, which is the pressure chamber 11 of FIG. 1, from an outer chamber 18 having a lower pressure, in which the shaft 8 is mounted in an outer bearing 13, which is opposite the pressure chamber 11 is sealed by the following sealing system:
- the annular gap 17 is formed between two slide bearing shells 19 made of extremely hard, wear-resistant materials, which are elastically supported by O-rings 20 to compensate for misalignments in the radial direction.
- the first pressure reduction stage formed by the slide bearing shells 19 is followed in the axial direction by a feedback device 21 which transfers this leakage from the first sealing stage into the conveying process of the turbomachine, for which a separate pump 23 can be provided.
- a separate pump 23 can be provided.
- the feedback device 21 is seen in the axial direction downstream of a second sealing stage 22, which as a simple seal z. B. can be formed in the form of a lip seal.
- FIG. 3 shows a screw pump according to FIG. 1 with a sealing system according to the invention, shown only schematically, according to FIG. 2 and a pressure compensation device 24 according to the invention, which is additionally provided or be formed by a bladder accumulator.
- the pressure compensation device 24 ensures that the same pressure level prevails in the installation space as in the suction space 10. This arrangement is particularly advantageous in the case of changing pressures in the suction space 10, so as to minimize the pressure differences at the second sealing stage 22.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Details And Applications Of Rotary Liquid Pumps (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
- Rotary Pumps (AREA)
- Medicines Containing Plant Substances (AREA)
- Liquid Crystal Substances (AREA)
- Adhesives Or Adhesive Processes (AREA)
- Sealing With Elastic Sealing Lips (AREA)
- Sealing Of Bearings (AREA)
- Prostheses (AREA)
- Electrical Discharge Machining, Electrochemical Machining, And Combined Machining (AREA)
- Mechanical Sealing (AREA)
Abstract
Description
Die Erfindung betrifft eine fluidführende Maschine, insbesondere Pumpe, mit einem in einem stillstehenden Gehäuseteil innerhalb eines Ringspaltes rotierenden Bauteil, wobei das stillstehende Gehäuseteil einen höheren Produktdruck aufweisenden Innenraum von einem einen niedrigeren Druck aufweisenden Außenraum trennt, in dem das rotierende Bauteil in einer Außenlagerung gelagert ist, die gegenüber dem Innenraum über ein Dichtungssystem abgedichtet ist.The invention relates to a fluid-carrying machine, in particular a pump, with a component rotating in a stationary housing part within an annular gap, the stationary housing part separating an interior having a higher product pressure from an exterior having a lower pressure, in which the rotating component is mounted in an external bearing , which is sealed from the interior by a sealing system.
Insbesondere betrifft die Erfindung eine Schraubenspindelpumpe mit zumindest einer Förderschraube, die von einem Gehäuse umschlossen ist, das zumindest einen Saugstutzen und zumindest einen Druckstutzen aufweist, wobei der Saugstutzen mit einem der Förderschraube vorgeschalteten Saugraum und der Druckstutzen mit einem der Förderschraube nachgeordneten Druckraum in Verbindung stehen, der Einrichtungen zur Separierung der jeweiligen Flüssigkeitsphase von der Gasphase des aus der Förderschraube austretenden Mediumstromes sowie einen unteren Abschnitt zur Aufnahine von zumindest einer Teilmenge der separierten Flüssigkeitsphase aufweist, wobei an diesem unteren Druckraumabschnitt eine Flüssigkeits-Kurzschlußleitung angeschlossen ist, die mit dem Saugraum in Verbindung steht und zusammen mit den Förderelementen einen geschlossenen Umlauf für eine zur permanenten Abdichtung erforderlichen Flüssigkeitsmenge bildet. Eine derartige Ausführungsform läßt sich der DE 43 16 735 C2 entnehmen.In particular, the invention relates to a screw pump with at least one feed screw, which is enclosed by a housing which has at least one suction port and at least one pressure port, the suction port being connected to a suction space upstream of the feed screw and the pressure port being connected to a pressure space downstream of the feed screw, of the devices for separating the respective liquid phase from the gas phase of the medium stream emerging from the feed screw and has a lower section for receiving at least a portion of the separated liquid phase, a liquid short-circuit line being connected to this lower pressure chamber section communicates with the suction chamber and, together with the conveying elements, forms a closed circuit for a quantity of liquid required for permanent sealing. Such an embodiment can be found in DE 43 16 735 C2.
Für die Abdichtung rotierender Wellen sind zahlreiche Dichtungssysteme entwickelt worden, die sich jedoch bei Maschinen der eingangs definierten Bauart als nachteilig erwiesen haben. Die Nachteile bei berührungslosen Labyrinthdichtungen liegen in deren hoher Leckage bedingt durch relativ große Spalte sowie darin, daß keine Druckdifferenzen an der Wellendurchführung ertragbar sind. Lippendichtringe ertragen nur geringe Druckdifferenzen bis maximal 5 bar an der Wellendurchführung. Weichpackungen weisen ebenfalls relativ hohe Leckagen auf, erfordern einen hohen Wartungsaufwand und entwickeln bei größeren Drehzahlen hohe Wärme. Die im Pumpenbau des gehobenen Niveaus eingesetzten Gleitringdichtungen erweisen sich hinsichtlich ihres komplexen Aufbaus und ihrer schwierigen Inbetriebnahme als nachteilig.Numerous sealing systems have been developed for sealing rotating shafts, but these have proven to be disadvantageous for machines of the type defined at the outset. The disadvantages of contactless labyrinth seals are their high leakage due to the relatively large gaps and the fact that no pressure differences on the shaft bushing can be tolerated. Lip seals only tolerate small pressure differences of up to 5 bar at the shaft bushing. Soft packs also have relatively high leakages, require a high level of maintenance and develop high heat at higher speeds. The mechanical seals used in high-level pump construction prove to be disadvantageous in terms of their complex structure and difficult commissioning.
Der Erfindung liegt die Aufgabe zugrunde, eine Maschine der eingangs beschriebenen Bauart mit einem verbesserten Abdichtsystem für das rotierende Bauteil zu entwickeln.The invention has for its object to develop a machine of the type described above with an improved sealing system for the rotating component.
Ausgehend von der eingangs beschriebenen Maschine wird diese Aufgabe gemäß der Erfindung dadurch gelöst, daß der Ringspalt zwischen zwei aus extrem harten, verschließfesten Werkstoffen bestehenden Gleitlagerschalen gebildet ist, die nach dem Wirkprinzip eines Radial-Gleitlagers eine erste Druckabbaustufe bilden, der in axialer Richtung eine die Leckage aus dieser ersten Dichtungsstufe in den Förderprozeß der Strömungsmaschine zurückführende Rückführeinrichtung nachgeschaltet ist, der in axialer Richtung eine zweite Dichtungsstufe nachgeordnet ist, die als einfache Dichtung in Form eines Lippendichtringes und/oder einer einfachen Gleitringdichtung ausgebildet ist.Starting from the machine described above, this object is achieved according to the invention in that the annular gap is formed between two extremely hard, wear-resistant materials slide bearing shells, which form a first pressure reduction stage according to the principle of action of a radial slide bearing, the one in the axial direction Leakage from this first sealing stage in the conveying process of the turbomachine returning device is connected downstream, which is followed by a second sealing stage in the axial direction, which is designed as a simple seal in the form of a lip seal and / or a simple mechanical seal.
Erfindungsgemäß wird somit ein zweistufiges Dichtungssystem vorgesehen. Die erste Stufe dient dem Druckabbau und bedient sich des Wirkprinzips eines Radial-Gleitlagers mit Aufbau eines hydrodynamischen Schinierkeils. Die Gleitlagerschalen können aus massiver Industriekeramik (z. B. auf Aluminiumoxydbasis oder Zirkonoxydbasis), aus massiven Hartmetallen (z. B. auf Siliziumkarbidbasis oder Wolframkarbidbasis) oder aber aus beschichteten Metallen (z. B. Hartverchromung, Wolframkarbid- oder Chromoxydbeschichtung) bestehen. Der Aufbau dieser ersten Dichtungsstufe hat den Vorteil, daß einerseits aus der Flüssigkeit des Fördermediums ein wirksamer hydrodynamischer Schmierkeil aufgebaut wird, daß andererseits jedoch etwaige, in den Ringspalt eingedrungene Partikel durch die extreme Härte und Verschleißfestigkeit der Gleitlagerschalen zwischen diesen einfach zerrieben werden.According to the invention, a two-stage sealing system is thus provided. The first stage is used to reduce pressure and uses the principle of action of a radial plain bearing with the construction of a hydrodynamic wedge. The plain bearing shells can be made from solid industrial ceramics (e.g. based on aluminum oxide or zirconium oxide), from solid hard metals (e.g. based on silicon carbide or tungsten carbide) or from coated metals (e.g. hard chrome plating, tungsten carbide or chromium oxide coating). The structure of this first sealing stage has the advantage that, on the one hand, an effective hydrodynamic lubricating wedge is built up from the liquid in the pumped medium, but, on the other hand, any particles that have penetrated into the annular gap are simply ground between them due to the extreme hardness and wear resistance of the plain bearing shells.
Zum Ausgleich von Fluchtungsfehlern ist es zweckmäßig, die Gleitlagerschalen in radialer Richtung elastisch zu lagern, z. B. in O-Ringen.To compensate for misalignment, it is advisable to elastically mount the plain bearing shells in the radial direction, for. B. in O-rings.
Die Rückführung der Leckage der ersten Dichtungsstufe kann z. B. durch geeignetes Druckgefälle zwischen Auslaß- und Einlaßseite der Maschine (bei auslaßseitiger Anordnung der Abdichtung) oder z. B. durch externe Hilfsmittel wie z. B. einer Pumpe (bei einlaßseitiger Anordnung der Abdichtung) erfolgen.The feedback of the leakage of the first sealing stage can e.g. B. by suitable pressure drop between the outlet and inlet side of the machine (with the outlet-side arrangement of the seal) or z. B. by external tools such. B. a pump (with inlet-side arrangement of the seal).
Geht man von einer Schraubenspindelpumpe der eingangs beschriebenen Bauart aus, dann ist es besonders vorteilhaft, die Leckage-Rückführeinrichtung an die Flüssigkeits-Kurzschlußleitung anzuschließen.Assuming a screw pump of the type described at the outset, it is particularly advantageous to connect the leakage feedback device to the liquid short-circuit line.
Die erfindungsgemäß vorgesehene zweite Dichtungsstufe minimiert zum Schutz der Umwelt oder mechanischer Funktionselemente die Leckage bei geringsten Differenzdrücken. Dabei kann die zweite Dichtungsstufe als einfaches Dichtungssystem in Form eines Lippendichtringes oder einer einfach wirkenden Gleitringdichtung ausgebildet sein. Je nach Anwendungserfordernis kann die zweite Dichtungsstufe auch als Mehrfachschaltung von Dichtsystemen herkömmlicher Bauart ausgebildet sein z. B. als Lippendichtring mit nachgeschalteter Gleitringdichtung oder aber als V-Ring mit nachgeschaltetem Lippendichtring und nachgeschalteter Gleitringdichtung.The second sealing stage provided according to the invention minimizes the leakage at the lowest differential pressures in order to protect the environment or mechanical functional elements. The second sealing stage can be designed as a simple sealing system in the form of a lip sealing ring or a single-acting mechanical seal. Depending on the application requirement, the second Seal stage can also be designed as a multiple circuit of sealing systems of conventional design z. B. as a lip seal with a downstream mechanical seal or as a V-ring with a downstream lip seal and a downstream mechanical seal.
Weitere Merkmale der Erfindung sind Gegenstand der Unteransprüche und werden in Verbindung mit weiteren Vorteilen der Erfindung anhand eines Ausführungsbeispieles näher erläutert.Further features of the invention are the subject of the dependent claims and are explained in connection with further advantages of the invention using an exemplary embodiment.
In Figur 2 ist eine als Beispiel dienende Ausführungsform der Erfindung dargestellt. Es zeigen
- Figur 1
- als Stand der Technik eine Schraubenspindelpumpe im Längsschnitt;
-
Figur 2 - in gegenüber Figur 1 vergrößertem Maßstab ein erfindungsgemäßes Abdichtsystem im - bezogen auf Figur 1 - rechten Lagerbereich einer Förderschraube und
-
Figur 3 - Die Schraubenspindelpumpe gemäß Figur 1 mit einer erfindungsgemäßen Druckausgleichseinrichtung.
- Figure 1
- as prior art, a screw pump in longitudinal section;
- Figure 2
- on an enlarged scale compared to FIG. 1, a sealing system according to the invention in the - in relation to FIG
- Figure 3
- The screw pump according to FIG. 1 with a pressure compensation device according to the invention.
Figur 1 zeigt eine vorbekannte (siehe DE 43 16 735 C2) Schraubenspindelpumpe, die als Förderelemente zwei berührungslos ineinanderkämmende, gegenläufige Förderschraubenpaare besitzt, die jeweils eine rechtsgängige Förderschraube 1 sowie eine linksgängige Förderschraube 2 umfassen. Die ineinandergreifenden Förderschrauben bilden zusammen mit dem sie umschließenden Gehäuse 3 einzeln abgeschlossene Förderkammern. Die Drehmomentübertragung von der Antriebs- auf die getriebene Welle erfolgt durch ein außerhalb des Pumpengehäuses 3 angeordnetes Zahnradgetriebe 4. Das Pumpengehäuse 3 weist einen Saugstutzen 5 sowie einen Druckstutzen 6 auf. Das der Pumpe durch den Saugstutzen 5 zufließende Medium 9 wird im Pumpengehäuse 3 in zwei Teilströme dem jeweils mittigen Saugraum 10 zugeführt, der der zugeordneten Förderschraube 1 bzw. 2 vorgeschaltet ist. Diesen Förderschrauben nachgeschaltet ist jeweils ein Druckraum 11, der axial nach außen durch jeweils eine Wellendichtung 12 abgeschlossen ist, die zur Abdichtung einer Außenlagerung 13 dient.Figure 1 shows a previously known (see DE 43 16 735 C2) screw pump, which has two contactless intermeshing, opposing pairs of conveying screws as conveying elements, each comprising a right-handed screw 1 and a left-
Am tiefsten Punkt des Druckraumes 11 ist eine Flüssigkeits-Kurzschlußleitung 14 angeschlossen, die mit dem Saugraum 10 in Verbindung steht. Der druckseitig aus dem geförderten Flüssigkeits-Gas-Gemisch separierte und dosiert in den Ansaugbereich zurückgeführte Teil-Flüssigkeitsvolumenstrom ist mit dem Pfeil 15 gekennzeichnet und wird als Flüssigkeitsumlauf wieder vom Saugraum 10 in den Druckraum 11 gefördert.At the lowest point of the
Der Flüssigkeitspegel im Pumpengehäuse 3 bzw. Druckraum 11 kann in der Regel unterhalb der Wellen 7, 8 liegen. Die Benetzung der Wellendichtungen 12 in Folge der direkten Anströmung reicht in der Regel für eine ausreichende Schmierung dieser Wellendichtungen 12 aus.The liquid level in the
Figur 2 zeigt ein Ausführungsbeispiel für die Erfindung. In einem stillstehenden Gehäuseteil 16 rotiert innerhalb eines Ringspaltes 17 ein Bauteil, bei dem es sich um die Welle 8 der Figur 1 handelt. Das stillstehende Gehäuseteil 16 trennt einen höheren Produktdruck aufweisenden Innenraum, bei dem es sich um den Druckraum 11 der Figur 1 handelt, von einem einen niedrigeren Druck aufweisenden Außenraum 18, in dem die Welle 8 in einer Außenlagerung 13 gelagert ist, die gegenüber dem Druckraum 11 über folgendes Dichtungssystem abgedichtet ist:Figure 2 shows an embodiment of the invention. In a
Der Ringspalt 17 ist zwischen zwei aus extrem harten, verschleißfesten Werkstoffen bestehenden Gleitlagerschalen 19 gebildet, die zum Ausgleich von Fluchtungsfehlern in radialer Richtung mit Hilfe von O-Ringen 20 elastisch gelagert sind. Für die den Ringspalt 17 durchströmende Leckage ist der durch die Gleitlagerschalen 19 gebildeten ersten Druckabbaustufe in axialer Richtung eine Rückführeinrichtung 21 nachgeschaltet, die diese Leckage aus der ersten Dichtungsstufe in den Förderprozeß der Strömungsmaschine zurückführt, wofür eine separate Pumpe 23 vorgesehen werden kann. Bei einer Anwendung des erfindungsgemäßen Dichtungssystems bei einer Schraubenspindelpumpe gemäß Figur 1 wäre es zweckmäßig, die Leckage-Rückführeinrichtung 21 an die in Figur 1 eingezeichnete Flüssigkeits-Kurzschlußleitung 14 anzuschließen.The
Der Rückführeinrichtung 21 ist in axialer Richtung gesehen eine zweite Dichtungsstufe 22 nachgeordnet, die als einfache Dichtung z. B. in Form eines Lippendichtringes ausgebildet sein kann.The
Figur 3 zeigt eine Schraubenspindelpumpe gemäß Figur 1 mit einem erfindungsgemäßen, nur schematisch angedeuteten Abdichtsystem gemäß Figur 2 und einer erfindungsgemäßen, zusätzlich vorgesehenen Druckausgleichseinrichtung 24. Letztere ist in eine den Einbauraum der Außenlagerung 13 mit dem Saugraum 10 verbindende Leitung 25 geschaltet und kann durch eine Membrane oder aber durch einen Blasenspeicher gebildet sein. Die Druckausgleichseinrichtung 24 sorgt dafür, daß in dem genannten Einbauraum das jeweils gleiche Druckniveau herrscht wie im Saugraum 10. Diese Anordnung ist bei wechselnden Drücken im Saugraum 10 besonders vorteilhaft, um so die Druckdifferenzen an der zweiten Dichtungsstufe 22 zu minimieren.FIG. 3 shows a screw pump according to FIG. 1 with a sealing system according to the invention, shown only schematically, according to FIG. 2 and a
Claims (10)
Priority Applications (13)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| AT98106690T ATE230070T1 (en) | 1998-04-11 | 1998-04-11 | WEAR RING SEAL |
| ES98106690T ES2187848T3 (en) | 1998-04-11 | 1998-04-11 | MACHINE DRIVING FLUIDS. |
| EP98106690A EP0955466B1 (en) | 1998-04-11 | 1998-04-11 | Annular gap seal |
| DK98106690T DK0955466T3 (en) | 1998-04-11 | 1998-04-11 | Seal for annular slot |
| DE59806719T DE59806719D1 (en) | 1998-04-11 | 1998-04-11 | Split ring seal |
| RU98123617/06A RU2218480C2 (en) | 1998-04-11 | 1998-12-28 | Fluid media handling machine (versions) |
| JP00493399A JP4152513B2 (en) | 1998-04-11 | 1999-01-12 | Liquid feeder |
| CA002262849A CA2262849C (en) | 1998-04-11 | 1999-02-23 | Improved sealing system for rotating component of a pump |
| NO19990860A NO323251B1 (en) | 1998-04-11 | 1999-02-23 | Spalteringtetning |
| KR10-1999-0008053A KR100527525B1 (en) | 1998-04-11 | 1999-03-11 | Sealing system for rotating component of a pump |
| US09/272,167 US6129533A (en) | 1998-04-11 | 1999-03-18 | Sealing system for rotating component of a pump |
| BR9902040-8A BR9902040A (en) | 1998-04-11 | 1999-04-12 | Fluid conducting machine. |
| CN99105562A CN1131377C (en) | 1998-04-11 | 1999-04-12 | Slit ring seal |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| EP98106690A EP0955466B1 (en) | 1998-04-11 | 1998-04-11 | Annular gap seal |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| EP0955466A1 true EP0955466A1 (en) | 1999-11-10 |
| EP0955466B1 EP0955466B1 (en) | 2002-12-18 |
Family
ID=8231756
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| EP98106690A Expired - Lifetime EP0955466B1 (en) | 1998-04-11 | 1998-04-11 | Annular gap seal |
Country Status (13)
| Country | Link |
|---|---|
| US (1) | US6129533A (en) |
| EP (1) | EP0955466B1 (en) |
| JP (1) | JP4152513B2 (en) |
| KR (1) | KR100527525B1 (en) |
| CN (1) | CN1131377C (en) |
| AT (1) | ATE230070T1 (en) |
| BR (1) | BR9902040A (en) |
| CA (1) | CA2262849C (en) |
| DE (1) | DE59806719D1 (en) |
| DK (1) | DK0955466T3 (en) |
| ES (1) | ES2187848T3 (en) |
| NO (1) | NO323251B1 (en) |
| RU (1) | RU2218480C2 (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2008116590A1 (en) * | 2007-03-23 | 2008-10-02 | Ghh Rand Schraubenkompressoren Gmbh | Sealing ring for shaft seals |
| DE202017107379U1 (en) | 2017-12-04 | 2017-12-18 | SKF Lubrication System Germany GmbH | Grease pump |
| DE102017221847A1 (en) | 2017-12-04 | 2019-06-06 | Skf Lubrication Systems Germany Gmbh | Grease pump and method for utilization of leakage grease of a grease pump |
Families Citing this family (13)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2002033262A1 (en) | 2000-10-18 | 2002-04-25 | Leybold Vakuum Gmbh | Multi-stage helical screw rotor |
| GB2371838B (en) * | 2001-02-02 | 2004-07-21 | Federal Mogul Rpb Ltd | Thrust Bearing Arrangement |
| US20080169157A1 (en) * | 2002-12-02 | 2008-07-17 | Wyker Christopher A | Lip seal lubrication reservoir and method of level control |
| CN1536801B (en) * | 2003-04-07 | 2010-04-28 | 华为技术有限公司 | Medium access control layer treatment unit of network side and user side |
| ZA200507096B (en) | 2004-09-07 | 2006-06-28 | Crane John Inc | Sealing system for slurry pump |
| WO2007000815A1 (en) * | 2005-06-29 | 2007-01-04 | Mayekawa Mfg. Co., Ltd | Oil supply method and device for two-stage screw compressor, and method of operating refrigeration device |
| US20080003099A1 (en) * | 2006-06-30 | 2008-01-03 | Honeywell International, Inc. | Closed bias air film riding seal in event of housing breach for shared engine lubrication accessory gearboxes |
| US8342156B2 (en) * | 2009-08-27 | 2013-01-01 | O'shea Fergal Michael | Bearing arrangement for a pump |
| US20120306156A1 (en) * | 2011-06-01 | 2012-12-06 | Alma Products Company | Compressor seal |
| DE102012001700B4 (en) * | 2012-01-31 | 2013-09-12 | Jung & Co. Gerätebau GmbH | Two-spindle screw pump in single-entry design |
| USD749138S1 (en) | 2014-12-19 | 2016-02-09 | Q-Pumps S.A. de C.V. | Twin screw pump |
| CN106481558B (en) * | 2015-08-27 | 2018-11-16 | 上海伊莱茨真空技术有限公司 | A kind of three lip oil sealing sealing systems for Roots vaccum pump |
| DE102020124392A1 (en) * | 2020-09-18 | 2022-03-24 | Itt Bornemann Gmbh | CLEARANCE ADJUSTMENT FOR TWIN SCREW PUMPS |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US2710581A (en) * | 1951-10-26 | 1955-06-14 | New York Air Brake Co | Rotary pump |
| US2758548A (en) * | 1950-08-24 | 1956-08-14 | Edward A Rockwell | Rotary fluid displacement device and mechanism therefor |
| DE2740161A1 (en) * | 1976-09-04 | 1978-03-16 | Howden Compressors Ltd | IMPROVEMENTS TO AND RELATING TO COMPRESSORS |
| GB2138074A (en) * | 1983-04-09 | 1984-10-17 | Glyco Antriebstechnik Gmbh | A hydraulic pump |
| DE4316735A1 (en) * | 1993-05-19 | 1994-11-24 | Bornemann J H Gmbh & Co | Pumping method for operating a multi-phase screw pump and pump |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US1673259A (en) * | 1926-03-11 | 1928-06-12 | Stacold Corp | Pump |
| US2549633A (en) * | 1945-12-22 | 1951-04-17 | Metals & Controls Corp | Gas burner ignition and safety control system |
| US3527507A (en) * | 1968-02-12 | 1970-09-08 | Garlock Inc | Unitary bearing element with improved,integral scraper-sealing lip |
| US3575426A (en) * | 1968-06-24 | 1971-04-20 | Caterpillar Tractor Co | Pressurized sealing arrangement |
| NL162721C (en) * | 1969-02-12 | 1980-06-16 | Cerpelli Orazio | SCREW PUMP. |
| US3589843A (en) * | 1969-02-14 | 1971-06-29 | Warren Pumps Inc | Rotary pump with intermeshing helical ribs |
| GB1317435A (en) * | 1969-06-05 | 1973-05-16 | Turnbull Marine Design | Ship propeller shaft stern bearing arrangements |
| JPS5951190A (en) * | 1982-09-17 | 1984-03-24 | Hitachi Ltd | Oil thrower device of oil-free screw compressor |
| GB2165890B (en) * | 1984-10-24 | 1988-08-17 | Stothert & Pitt Plc | Improvements in pumps |
| GB2182393A (en) * | 1985-11-04 | 1987-05-13 | Ngk Insulators Ltd | Intermeshing screw pump |
| JPS631772A (en) * | 1986-06-20 | 1988-01-06 | Kobe Steel Ltd | Vacuum pump and running method thereof |
| JP2515831B2 (en) * | 1987-12-18 | 1996-07-10 | 株式会社日立製作所 | Screen vacuum pump |
| JPH03110138A (en) * | 1989-09-25 | 1991-05-10 | Kobe Steel Ltd | Rim changer apparatus in tire uniformity machine |
| JP3344825B2 (en) * | 1994-05-24 | 2002-11-18 | 栃木富士産業株式会社 | Sealing device for screw supercharger |
-
1998
- 1998-04-11 DK DK98106690T patent/DK0955466T3/en active
- 1998-04-11 EP EP98106690A patent/EP0955466B1/en not_active Expired - Lifetime
- 1998-04-11 DE DE59806719T patent/DE59806719D1/en not_active Expired - Lifetime
- 1998-04-11 AT AT98106690T patent/ATE230070T1/en active
- 1998-04-11 ES ES98106690T patent/ES2187848T3/en not_active Expired - Lifetime
- 1998-12-28 RU RU98123617/06A patent/RU2218480C2/en not_active IP Right Cessation
-
1999
- 1999-01-12 JP JP00493399A patent/JP4152513B2/en not_active Expired - Fee Related
- 1999-02-23 CA CA002262849A patent/CA2262849C/en not_active Expired - Fee Related
- 1999-02-23 NO NO19990860A patent/NO323251B1/en not_active IP Right Cessation
- 1999-03-11 KR KR10-1999-0008053A patent/KR100527525B1/en not_active IP Right Cessation
- 1999-03-18 US US09/272,167 patent/US6129533A/en not_active Expired - Fee Related
- 1999-04-12 BR BR9902040-8A patent/BR9902040A/en not_active IP Right Cessation
- 1999-04-12 CN CN99105562A patent/CN1131377C/en not_active Expired - Fee Related
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US2758548A (en) * | 1950-08-24 | 1956-08-14 | Edward A Rockwell | Rotary fluid displacement device and mechanism therefor |
| US2710581A (en) * | 1951-10-26 | 1955-06-14 | New York Air Brake Co | Rotary pump |
| DE2740161A1 (en) * | 1976-09-04 | 1978-03-16 | Howden Compressors Ltd | IMPROVEMENTS TO AND RELATING TO COMPRESSORS |
| GB2138074A (en) * | 1983-04-09 | 1984-10-17 | Glyco Antriebstechnik Gmbh | A hydraulic pump |
| DE4316735A1 (en) * | 1993-05-19 | 1994-11-24 | Bornemann J H Gmbh & Co | Pumping method for operating a multi-phase screw pump and pump |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2008116590A1 (en) * | 2007-03-23 | 2008-10-02 | Ghh Rand Schraubenkompressoren Gmbh | Sealing ring for shaft seals |
| DE202017107379U1 (en) | 2017-12-04 | 2017-12-18 | SKF Lubrication System Germany GmbH | Grease pump |
| DE102017221847A1 (en) | 2017-12-04 | 2019-06-06 | Skf Lubrication Systems Germany Gmbh | Grease pump and method for utilization of leakage grease of a grease pump |
Also Published As
| Publication number | Publication date |
|---|---|
| CN1232142A (en) | 1999-10-20 |
| CA2262849A1 (en) | 1999-10-11 |
| BR9902040A (en) | 2000-02-22 |
| KR100527525B1 (en) | 2005-11-09 |
| EP0955466B1 (en) | 2002-12-18 |
| ATE230070T1 (en) | 2003-01-15 |
| CN1131377C (en) | 2003-12-17 |
| NO323251B1 (en) | 2007-02-12 |
| KR19990082721A (en) | 1999-11-25 |
| DE59806719D1 (en) | 2003-01-30 |
| JPH11303772A (en) | 1999-11-02 |
| JP4152513B2 (en) | 2008-09-17 |
| DK0955466T3 (en) | 2003-03-03 |
| NO990860L (en) | 1999-10-12 |
| RU2218480C2 (en) | 2003-12-10 |
| US6129533A (en) | 2000-10-10 |
| CA2262849C (en) | 2004-11-30 |
| NO990860D0 (en) | 1999-02-23 |
| ES2187848T3 (en) | 2003-06-16 |
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