EP0955466B1 - Annular gap seal - Google Patents
Annular gap seal Download PDFInfo
- Publication number
- EP0955466B1 EP0955466B1 EP98106690A EP98106690A EP0955466B1 EP 0955466 B1 EP0955466 B1 EP 0955466B1 EP 98106690 A EP98106690 A EP 98106690A EP 98106690 A EP98106690 A EP 98106690A EP 0955466 B1 EP0955466 B1 EP 0955466B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- pressure
- compartment
- machine according
- sealing
- stage
- 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.)
- Expired - Lifetime
Links
- 238000007789 sealing Methods 0.000 claims abstract description 31
- 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
- 238000009434 installation Methods 0.000 claims description 3
- 238000000034 method Methods 0.000 claims description 3
- 238000011144 upstream manufacturing Methods 0.000 claims description 3
- 239000012071 phase Substances 0.000 claims description 2
- 239000012530 fluid Substances 0.000 abstract 1
- 230000005540 biological transmission Effects 0.000 description 2
- 238000010276 construction Methods 0.000 description 2
- 230000001050 lubricating effect Effects 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
- 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
- 238000005461 lubrication Methods 0.000 description 1
- 238000012423 maintenance Methods 0.000 description 1
- 239000012528 membrane Substances 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
- HBMJWWWQQXIZIP-UHFFFAOYSA-N silicon carbide Chemical compound [Si+]#[C-] HBMJWWWQQXIZIP-UHFFFAOYSA-N 0.000 description 1
- 229910010271 silicon carbide Inorganic materials 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 Pump, with one in a stationary housing part inside an annular gap rotating component, the stationary Housing part with a higher product pressure interior separates from a lower pressure outside space, in which the rotating component is stored in an external bearing is sealed from the interior via a sealing system is.
- the invention relates to a screw pump with at least one feed screw, which was enclosed by a housing is that at least one suction nozzle and at least has a pressure port, the suction port with one of the Conveyor screw upstream suction chamber and the pressure nozzle with a pressure chamber downstream of the screw stand, the facilities for separating the respective liquid phase from the gas phase of the emerging from the screw Medium flow and a lower section for recording of at least a subset of the separated liquid phase has, at this lower pressure chamber section a liquid short-circuit line is connected with communicates with the suction chamber and together with the conveyor elements a closed circuit for permanent sealing forms the required amount of liquid.
- a liquid short-circuit line is connected with communicates with the suction chamber and together with the conveyor elements a closed circuit for permanent sealing forms the required amount of liquid.
- the invention has for its object a machine of the beginning described design with an improved sealing system to develop for the rotating component.
- a two-stage sealing system is thus provided.
- the first stage is used to reduce pressure and is used of the principle of action of a radial plain bearing with the construction of a hydrodynamic lubricating wedge.
- the plain bearing shells can solid industrial ceramics (e.g. based on aluminum oxide or Zirconium oxide base), made of solid hard metals (e.g. based on silicon carbide) or tungsten carbide base) or from coated Metals (e.g. hard chrome plating, tungsten carbide or chromium oxide coating) consist.
- This first sealing stage has the advantage that on the one hand from the liquid of the medium built an effective hydrodynamic lubricating wedge is that, on the other hand, however, any penetrated into the annular gap Particles due to the extreme hardness and wear resistance the plain bearing shells simply grated between them become.
- the feedback of the leakage of the first sealing stage can e.g. B. due to a suitable pressure drop between the outlet and inlet side the machine (with sealing arrangement on the outlet side) or z. B. by external tools such. B. a pump (at the inlet side Arrangement of the seal).
- the second sealing stage provided according to the invention is minimized to protect the environment or mechanical functional elements Leakage at the lowest differential pressures.
- the second Sealing level as a simple sealing system in the form of a lip seal or a single-acting mechanical seal be trained.
- the second Sealing stage also as a multiple circuit of sealing systems more conventional Be designed z. B. as a lip seal downstream mechanical seal or as a V-ring with downstream lip seal and downstream mechanical seal.
- FIG. 1 shows a previously known (see DE 43 16 735 C2) screw pump, the two contactless intermeshing conveying elements, has opposite pairs of conveyor screws, the one right-hand screw 1 and one left-hand screw Include feed screw 2.
- the interlocking conveyor screws form together with the enclosing housing 3 individually closed delivery chambers.
- the torque transmission from the drive to the driven shaft is done by a Gear transmission 4 arranged outside the pump housing 3.
- the pump housing 3 has a suction nozzle 5 and a pressure nozzle 6 on. That flowing to the pump through the suction nozzle 5
- Medium 9 is in the pump housing 3 in two partial flows each central suction chamber 10 supplied to the associated feed screw 1 or 2 is connected upstream.
- This screw downstream is a pressure chamber 11, which is axially outward is completed by a shaft seal 12 each serves to seal an outer bearing 13.
- a liquid short-circuit line 14 connected to the suction chamber 10 in connection stands.
- the pressure side from the pumped liquid-gas mixture separated and dosed back into the suction area Partial liquid volume flow is marked with arrow 15 and is used as a liquid recirculation from the suction chamber 10 promoted in the pressure chamber 11.
- the liquid level in the pump housing 3 or pressure chamber 11 can are usually below the waves 7, 8.
- FIG. 2 shows an embodiment of the invention.
- one stationary housing part 16 rotates within an annular gap 17 is a component which is the shaft 8 of the figure 1 acts.
- the stationary housing part 16 separates a higher one Product pressure interior, which is the Pressure chamber 11 of Figure 1 is a lower one Pressure-bearing outer space 18, in which the shaft 8 in a External bearing 13 is mounted, which is opposite the pressure chamber 11 is sealed by the following sealing system:
- the annular gap 17 is between two extremely hard, wear-resistant Materials existing slide bearing shells 19 formed, to compensate for misalignments in radial Direction with the help of O-rings 20 are mounted elastically.
- For the leakage flowing through the annular gap 17 is that caused by the Slide bearing shells 19 formed the first pressure reduction stage in the axial Directed a feedback device 21, the this leakage from the first sealing stage in the conveying process of the turbomachine, for which purpose a separate pump 23 can be provided.
- a separate pump 23 can be provided.
- the feedback device 21 is seen in the axial direction second sealing stage 22 downstream, as a simple seal z. B. can be formed in the form of a lip seal.
- FIG 3 shows a screw pump according to Figure 1 with a sealing system according to the invention, only indicated schematically according to Figure 2 and an inventive, additionally provided Pressure equalization device 24.
- the latter is in the installation space the outer bearing 13 connecting the suction chamber 10 Line 25 switched and can through a membrane or be formed by a bladder accumulator.
- the pressure compensation device 24 ensures that in the installation space mentioned the same pressure level prevails as in the suction chamber 10. This Arrangement is special with changing pressures in the suction space 10 advantageous, so the pressure differences at the second Minimize seal level 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)
- Adhesives Or Adhesive Processes (AREA)
- Liquid Crystal Substances (AREA)
- Sealing With Elastic Sealing Lips (AREA)
- Sealing Of Bearings (AREA)
- Mechanical Sealing (AREA)
- Prostheses (AREA)
- Electrical Discharge Machining, Electrochemical Machining, And Combined Machining (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 Pump, with one in a stationary housing part inside an annular gap rotating component, the stationary Housing part with a higher product pressure interior separates from a lower pressure outside space, in which the rotating component is stored in an external bearing is sealed from the interior via a sealing system is.
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 Aufnahme 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 was enclosed by a housing is that at least one suction nozzle and at least has a pressure port, the suction port with one of the Conveyor screw upstream suction chamber and the pressure nozzle with a pressure chamber downstream of the screw stand, the facilities for separating the respective liquid phase from the gas phase of the emerging from the screw Medium flow and a lower section for recording of at least a subset of the separated liquid phase has, at this lower pressure chamber section a liquid short-circuit line is connected with communicates with the suction chamber and together with the conveyor elements a closed circuit for permanent sealing forms the required amount of liquid. Such 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.There are numerous sealing systems for sealing rotating shafts have been developed, but which are in machines of have initially proven to be disadvantageous. The Disadvantages with non-contact labyrinth seals lie in their high leakage due to relatively large gaps as well as that no pressure differences on the shaft bushing can be tolerated are. Lip seals only tolerate small pressure differences up to a maximum of 5 bar on the shaft bushing. Show soft packs also relatively high leakages, require a high Maintenance effort and develop high heat at higher speeds. The mechanical seals used in high-level pump construction prove themselves with regard to their complex structure and their difficult commissioning as a disadvantage.
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 a machine of the beginning described design with an improved sealing system to develop 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, verschleißfesten 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 at the beginning, this is Object achieved according to the invention in that the annular gap between two made of extremely hard, wear-resistant materials existing plain bearing shells is formed, which works on the principle of action of a radial plain bearing form a first pressure reduction stage, the one in the axial direction the leakage from this first Sealing stage in the conveying process of the turbomachine Feedback device is connected downstream in the axial Direction is a second sealing stage downstream, which as simple seal in the form of a lip seal and / or one simple mechanical seal is formed.
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 Schmierkeils. 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 is used of the principle of action of a radial plain bearing with the construction of a hydrodynamic lubricating wedge. The plain bearing shells can solid industrial ceramics (e.g. based on aluminum oxide or Zirconium oxide base), made of solid hard metals (e.g. based on silicon carbide) or tungsten carbide base) or from coated Metals (e.g. hard chrome plating, tungsten carbide or chromium oxide coating) consist. The structure of this first sealing stage has the advantage that on the one hand from the liquid of the medium built an effective hydrodynamic lubricating wedge is that, on the other hand, however, any penetrated into the annular gap Particles due to the extreme hardness and wear resistance the plain bearing shells simply grated between them become.
Zum Ausgleich von Fluchtungsfehlern ist es zweckmäßig, die Gleitlagerschalen in radialer Richtung elastisch zu lagern, z. B. in O-Ringen.To compensate for misalignments, it is advisable to use the To mount plain bearing shells elastically in the radial direction, z. 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. due to a suitable pressure drop between the outlet and inlet side the machine (with sealing arrangement on the outlet side) or z. B. by external tools such. B. a pump (at the 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.If you start from a screw pump of the type described above Type out, then it is particularly advantageous that Leakage feedback device to the liquid short-circuit line to join.
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 is minimized to protect the environment or mechanical functional elements Leakage at the lowest differential pressures. The second Sealing level as a simple sealing system in the form of a lip seal or a single-acting mechanical seal be trained. Depending on the application requirement, the second Sealing stage also as a multiple circuit of sealing systems more conventional Be designed z. B. as a lip seal downstream mechanical seal or as a V-ring with downstream lip seal and 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 in connection with further advantages of the invention explained in more detail 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 a 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 - based on FIG. 1 - right-hand bearing area of a conveyor screw and
- 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.FIG. 1 shows a previously known (see DE 43 16 735 C2) screw pump,
the two contactless intermeshing conveying elements,
has opposite pairs of conveyor screws, the
one right-
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 one
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.Figure 3 shows a screw pump according to Figure 1 with a
sealing system according to the invention, only indicated schematically
according to Figure 2 and an inventive, additionally provided
Claims (10)
- Fluid-conveying machine, in particular pump, having a component (8) which rotates in a stationary housing part (16) within an annular gap (17), the stationary housing part (16) separating an inner compartment (11), which is at a higher product pressure, from an outer compartment (18), which is at a lower pressure and in which the rotating component (8) is mounted in an outer bearing (13) which is sealed with respect to the inner compartment (11) by means of a sealing system (17, 19, 22), characterized in that the annular gap (17) is formed between two sliding bearing shells (19), which consists of extremely hard, wear-resistant materials, and, in accordance with the operating principle of a radial sliding bearing, form a first pressure reduction stage, downstream of which, in the axial direction, there is a return device (21) which returns the leakage from this first sealing stage into the delivery process of the machine and downstream of which, in the axial direction, there is a second sealing stage (22), which is designed as a simple seal in the form of a lip sealing ring and/or a simple sliding ring seal.
- Machine according to Claim 1, characterized in that the sliding bearing shells (19) are mounted elastically in the radial direction in order to compensate for alignment errors.
- Machine according to Claim 1 or 2, characterized in that the gap thickness of the annular gap (17) formed between the sliding bearing shells (19) is approximately 0.3 to 1.5% of the sliding-surface diameter.
- Machine according to Claim 1, 2 or 3, characterized in that the length of the sliding bearing shells (19) is approximately 20 - 60% of the sliding surface diameter.
- Machine according to one of the preceding claims, characterized in that the second sealing stage (22) is designed as a multiple connection of seals which comprises a V ring, a lip sealing ring and a sliding ring seal.
- Screw pump having at least one delivery screw (1, 2) which is surrounded by a housing (3) which has at least one suction connection piece (5) and at least one pressure connection piece (6), the suction connection piece (5) being in communication with a suction compartment (10) connected upstream of the delivery screw (1, 2) and the pressure connection piece (6) being in communication with a pressure compartment (11) which is arranged downstream of the delivery screw (1, 2) and has devices for separating the respective liquid phase from the gas phase of the flow of medium emerging from the delivery screw (1, 2) and a lower section for holding at least a partial quantity of the separated liquid phase, a liquid short-circuit line (14), which is in communication with the suction compartment (10) and, together with the delivery elements, forms a closed circuit for a quantity of liquid required for permanent sealing, being connected to this lower pressure-compartment section, according to one of the preceding claims, characterized in that the return device (21) is connected to the liquid short-circuit line (14).
- Machine according to Claim 6, characterized in that a pressure-compensation device (24), which produces a uniform pressure level, is provided between the installation compartment for the outer bearing (13) and the suction compartment (10).
- Machine according to Claim 7, characterized in that the pressure compensation device (24) is formed by a diaphragm.
- Machine according to Claim 7, characterized in that the pressure compensation device (24) is formed by a bubble store.
- Machine according to one of the preceding claims, characterized in that the return device (21) has a separate pump (23).
Priority Applications (13)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| EP98106690A EP0955466B1 (en) | 1998-04-11 | 1998-04-11 | Annular gap seal |
| ES98106690T ES2187848T3 (en) | 1998-04-11 | 1998-04-11 | MACHINE DRIVING FLUIDS. |
| DE59806719T DE59806719D1 (en) | 1998-04-11 | 1998-04-11 | Split ring seal |
| DK98106690T DK0955466T3 (en) | 1998-04-11 | 1998-04-11 | Seal for annular slot |
| AT98106690T ATE230070T1 (en) | 1998-04-11 | 1998-04-11 | WEAR 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 |
| NO19990860A NO323251B1 (en) | 1998-04-11 | 1999-02-23 | Spalteringtetning |
| CA002262849A CA2262849C (en) | 1998-04-11 | 1999-02-23 | Improved sealing system for rotating component of a pump |
| 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 EP0955466A1 (en) | 1999-11-10 |
| EP0955466B1 true 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) |
Families Citing this family (16)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP1327078B1 (en) | 2000-10-18 | 2009-05-06 | LEYBOLD VACUUM 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 |
| DE202007004292U1 (en) * | 2007-03-23 | 2008-07-31 | Ghh-Rand Schraubenkompressoren Gmbh | Seal for shaft seals |
| 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 |
| 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 |
| DE202017107379U1 (en) | 2017-12-04 | 2017-12-18 | SKF Lubrication System Germany GmbH | Grease pump |
| DE102020124392A1 (en) * | 2020-09-18 | 2022-03-24 | Itt Bornemann Gmbh | CLEARANCE ADJUSTMENT FOR TWIN SCREW PUMPS |
Family Cites Families (19)
| 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 |
| 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 |
| 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 |
| GB1570512A (en) * | 1976-09-04 | 1980-07-02 | Howden Compressors Ltd | Meshing-screw gas-compressing apparatus |
| JPS5951190A (en) * | 1982-09-17 | 1984-03-24 | Hitachi Ltd | Oil thrower device of oil-free screw compressor |
| DE3312868C2 (en) * | 1983-04-09 | 1986-03-20 | Glyco-Antriebstechnik Gmbh, 6200 Wiesbaden | Hydraulic pump |
| 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 |
| DE4316735C2 (en) * | 1993-05-19 | 1996-01-18 | Bornemann J H Gmbh & Co | Pumping method for operating a multi-phase screw pump and pump |
| 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 ES ES98106690T patent/ES2187848T3/en not_active Expired - Lifetime
- 1998-04-11 EP EP98106690A patent/EP0955466B1/en not_active Expired - Lifetime
- 1998-04-11 AT AT98106690T patent/ATE230070T1/en active
- 1998-04-11 DE DE59806719T patent/DE59806719D1/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 NO NO19990860A patent/NO323251B1/en not_active IP Right Cessation
- 1999-02-23 CA CA002262849A patent/CA2262849C/en not_active Expired - Fee Related
- 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 CN CN99105562A patent/CN1131377C/en not_active Expired - Fee Related
- 1999-04-12 BR BR9902040-8A patent/BR9902040A/en not_active IP Right Cessation
Also Published As
| Publication number | Publication date |
|---|---|
| NO990860D0 (en) | 1999-02-23 |
| EP0955466A1 (en) | 1999-11-10 |
| NO990860L (en) | 1999-10-12 |
| JP4152513B2 (en) | 2008-09-17 |
| CN1232142A (en) | 1999-10-20 |
| CA2262849A1 (en) | 1999-10-11 |
| RU2218480C2 (en) | 2003-12-10 |
| BR9902040A (en) | 2000-02-22 |
| ES2187848T3 (en) | 2003-06-16 |
| US6129533A (en) | 2000-10-10 |
| CN1131377C (en) | 2003-12-17 |
| DK0955466T3 (en) | 2003-03-03 |
| DE59806719D1 (en) | 2003-01-30 |
| NO323251B1 (en) | 2007-02-12 |
| CA2262849C (en) | 2004-11-30 |
| JPH11303772A (en) | 1999-11-02 |
| KR19990082721A (en) | 1999-11-25 |
| ATE230070T1 (en) | 2003-01-15 |
| KR100527525B1 (en) | 2005-11-09 |
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