EP0405160B1 - Screw rotor pump - Google Patents
Screw rotor pump Download PDFInfo
- Publication number
- EP0405160B1 EP0405160B1 EP90110215A EP90110215A EP0405160B1 EP 0405160 B1 EP0405160 B1 EP 0405160B1 EP 90110215 A EP90110215 A EP 90110215A EP 90110215 A EP90110215 A EP 90110215A EP 0405160 B1 EP0405160 B1 EP 0405160B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- bearing
- screw rotor
- rotor pump
- spindles
- spindle
- 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
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Classifications
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- 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
- F04C2/00—Rotary-piston machines or pumps
- F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
- F04C2/082—Details specially related to intermeshing engagement type machines or pumps
- F04C2/086—Carter
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- 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
- F04C2/00—Rotary-piston machines or pumps
- F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
- F04C2/12—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
- F04C2/14—Rotary-piston machines or pumps 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
- F04C2/16—Rotary-piston machines or pumps 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
- F04C2/165—Rotary-piston machines or pumps 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 having more than two rotary pistons with parallel axes
Definitions
- the invention relates to a screw pump with a drive spindle arranged in the interior of a pump housing and at least one sealing spindle parallel to the axis, and with an inlet and an outlet for a flow medium to be conveyed by the spindles.
- At least the sealing spindle is equipped with a peg-like bearing end and is preferably mounted in the pump cover.
- Such a screw pump with two sealing or running spindles flanking the drive spindle can be found, for example, in DE-PS 716 161; the bearing recesses for all spindles are located there in the pump cover and connected to the interior of the pump housing.
- US-A-2592476 reveals a screw pump with a pair of sealing spindles which pass through several axial housing parts.
- One of these housing parts has four bores, which are arranged around the drive spindle and both accommodate the pair of sealing spindles and two opposing short spindles.
- the temperature conditions, particularly in the spindle area, are of particular importance for the operation of such screw pumps, which is why the aim of this invention is to make the temperature uniform over the length of the pump rotor.
- the temperature conditions, particularly in the spindle area, are of particular importance for the operation of such screw pumps, which is why the aim of this invention is to make the temperature uniform over the length of the pump rotor.
- the spindles are surrounded by a tubular housing insert and this, with the pump housing surrounding it, delimits at least one annular space which is connected to the interior receiving the spindles by at least one opening.
- the annular space on the suction side against the interior and to provide the radial openings at its pressure end.
- the outlet should be provided at the suction-side end of the annular space.
- an inlet on the suction side is preferably arranged outside the housing insert in the radial region of the bearing of the spindles.
- the housing insert according to the invention is easy to manufacture and assemble. It can also be easily fitted with low-wear inserts on the inside.
- the free end face of the bearing bush with the bottom of the recess of the pump cover delimits a tight gap space connected to the interior of the screw pump, which is preferably connected to an extension of the interior via a radial line.
- the profile outlet of the sealing spindle is surrounded by a compensating bush, which strikes the shoulder of the sealing spindle with its pressure-side end.
- This compensating sleeve - which forms a control edge with its suction-side end - is adjoined by a shell made of low-wear material which is fixed in the bearing sleeve and which advantageously projects beyond the end face of the bearing journal; an end gap connected to the pressure chamber is desired between the end face of the bearing journal and the bottom of the bearing recess.
- the end gaps of the bearing journals should advantageously be connected to a transverse line by means of at least one line passing through the bearing bush. It has proven to be expedient to let a bore emanate from the bottom of the bearing bush, which bore connects to a sleeve penetrating that gap as part of the line.
- the pressure supply in the bearing bushes is sealed, but the bearing bushes themselves can be moved radially.
- the screw pump which is usually designed for lubricating fluids, at a function-critical point - in particular the hydrostatic axial thrust compensation, for example also when pumping water.
- the specific arrangement of cylindrical bearing bodies or bearing bushes into which the spindles are immersed up to a radial stop serves this purpose.
- the bearing body or bushing has an axial opening that connects the storage space - in which the spindle pin is immersed - with the pressure chamber of the pump.
- the connection of the pressure-carrying connection of the bearing sleeve is designed so that the fluid pressure is effective only on the cross section of the spindle pin.
- a minimal axial movement across the gap between the spindle and the axial collar can balance the axial thrust and hydraulic relief.
- the introduction of the pump pressure to compensate for the axial thrust is designed so that the pressure can be concentrated on only for the purpose described above.
- the bearing sleeve should move radially freely, ie be able to continuously adapt to the radial movement of the spindle.
- a non-positive rotation inhibition for example in the form of an elastic ring element, ensures that the bearing bush does not rotate, since otherwise the necessary seal between the bearing body and the pressure-carrying connection or line would not be provided.
- a screw pump 10 has, in the interior 12 of a pump housing 14 screwed onto a pump base 11, a drive spindle 18 flanked by two sealing or running spindles 16.
- the sealing or running spindles 16 are mounted on the suction side in a pump cover 20, the drive spindle 18 is connected on the drive side to a coaxial drive shaft journal 22.
- the drive shaft journal 22 passes through roller bearings 28 arranged in a bearing cover 24 - between a labyrinth ring 25 and a support disk 26 with a downstream lubrication chamber 27. That bearing cover 24 is connected to a drive-side pump cover 31 by means of cylinder screws 29 and with the interposition of a mechanical seal 30, 34, wherein the mechanical seal 30, 34 lies in a seal space 32.
- a compensating piston 36 surrounded by low-wear shells 35 and provided with throttle grooves can be recognized on a flange 38. This rests partly in the pump cover 31 and partly in the pump housing 14, the length a of which is approximately 270 mm.
- a compensating bushing 40 of length n which abuts a shoulder-like shoulder 42 of the spindle 16, is shrunk onto the suction-side bearing journal 17 of the two running spindles 16.
- This compensating bushing 40 faces with its suction-side end a bearing recess 44 of a bearing body or a bearing bush 46 and forms a control edge there for regulating the hydrostatic pressure.
- the control edge here lies opposite the edge of a shell 41 seated in the bearing recess 44 and made of particularly wear-resistant material.
- the length t of the shell 41 is greater than the free length of the bearing journal 17 and thus determines the width of an end gap 48 remaining between the suction-side end face 17 s of the bearing journal 17 and the bottom 45 of the bearing recess 44.
- An axial inlet bore 50 of the bearing bush opens into this 46; this inlet bore 50 is connected to a channel 54 of the suction-side pump cover 20 by means of a sleeve 53, which has an axial bore 52; the channels 54 of the spindle bearings are connected to one another by a blind bore 56 provided radially in the pump cover 20.
- FIG. 1 shows that said sleeve 53 bridges a gap space 58 of the 46 one hand, between the suction-side end of the bearing bush and the bottom of a pump cover 20 is formed 60 of a blind recess 58 receiving the same.
- This gap space 58 is connected via radial bores 59 to a cylindrical extension 13 of the interior 12 of the pump housing 14.
- an O-ring 62 can be seen as a sealant in the periphery of the bearing bush 46 - other O-rings respectively provided in ring grooves are also designated by 62.
- the pump housing 14 is designed such that a tubular housing insert 64 of length b of, for example, 190 mm surrounding the spindles 16, 18 rests on both sides of housing ribs 66, 66 s in such a way that an annular space 15 is formed between the housing insert 64 and the pump housing 14 suction-side housing rib 66 s is sealed to the interior 12 by means of an O-ring 62 and has passages 68 in the area of the other housing rib 66. Otherwise, the housing insert 64 is held with its pressure-side edge 64 d between the housing rib 66 and the flange 38.
- Material inserts 70 made of wear-resistant - preferably ceramic - material are provided between the housing insert 64 and the spindles 16, 18.
- the material inserts 70 are in themselves disk-like and are provided with receiving bores (not shown for reasons of clarity) for the spindles 16, 18 passing through them.
- Several of these material inserts 70 are arranged coaxially in the pump housing 14.
- the material inserts 70 are fixed by means of a plastic layer indicated at 71, which is introduced through bores 72 between the housing insert 64 and the material insert 70.
- the described annular space 15 is - as can be seen in FIG. 1 - connected to the blind bore 56 of the pump cover 20 by means of an axially parallel longitudinal bore 74 in the pump housing 14.
- FIG. 2 shows the suction space inlet 76 and - at the deepest of the annular space 15 - the outlet 78; between the two lies that housing insert 64, so that the fluid between the suction chamber inlet 76 and the outlet 78 is forced to flow through the passage 68 of the housing insert 64 into the annular space 15 and over almost the entire length b of the housing insert 64 to the outlet 78.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Rotary Pumps (AREA)
- Details And Applications Of Rotary Liquid Pumps (AREA)
Abstract
Description
Die Erfindung betrifft eine Schraubenspindelpumpe mit im Innenraum eines Pumpengehäuses angeordneter Antriebsspindel und wenigstens einer dazu achsparallelen Dichtspindel sowie mit einem Zulauf und einem Auslauf für ein von den Spindeln zu förderndes Strömungsmedium. Zumindest die Dichtspindel ist mit einem zapfenartigen Lagerende ausgestattet und bevorzugt im Pumpendeckel gelagert.The invention relates to a screw pump with a drive spindle arranged in the interior of a pump housing and at least one sealing spindle parallel to the axis, and with an inlet and an outlet for a flow medium to be conveyed by the spindles. At least the sealing spindle is equipped with a peg-like bearing end and is preferably mounted in the pump cover.
Eine derartige Schraubenspindelpumpe mit zwei die Antriebsspindel flankierenden Dicht- oder Laufspindeln kann beispielsweise der DE-PS 716 161 entnommen werden; die Lagerausnehmungen für alle Spindeln sind dort im Pumpendeckel angebracht sowie mit dem Innenraum des Pumpengehäuses verbunden.Such a screw pump with two sealing or running spindles flanking the drive spindle can be found, for example, in DE-PS 716 161; the bearing recesses for all spindles are located there in the pump cover and connected to the interior of the pump housing.
Die US-A-2592476 läßt eine Schraubenspindelpumpe mit einem Paar von Dichtspindeln erkennen, welche mehrere axiale Gehäuseteile durchsetzen. Eines dieser Gehäuseteile weist vier Bohrungen auf, welche um die der Antriebsspindel angeordnet sind und sowohl das Paar von Dichtspindeln aufnehmen als auch zwei einander gegenüberliegende Kurzspindeln.US-A-2592476 reveals a screw pump with a pair of sealing spindles which pass through several axial housing parts. One of these housing parts has four bores, which are arranged around the drive spindle and both accommodate the pair of sealing spindles and two opposing short spindles.
Bei Schraubenspindelpumpen bekannter Bauart mit zwei oder mehr Spindeln wird das Fördergut in durch die Spindeln und das sie umgebende Pumpengehäuse gebildeten Kammern bei Rotation der Spindeln axial bewegt. Der dabei als Folge des Druckaufbaus in Gegenrichtung entstehende Axialschub wird in der Regel durch die Spindeln einerseits und mittels eines Widerlagers auf der Gehäuseseite anderseits aufgenommen. Diese Lagerung hat sich bei der Förderung schmierender Fluide im Bereich niederer Förderdrücke bewährt, wobei deren Schmierwirkung diese eben so einfache wie betriebssichere Axiallagerung ermöglicht.In screw pumps of known type with two or more spindles, the material to be conveyed is moved axially in the chambers formed by the spindles and the pump housing surrounding them when the spindles rotate. The axial thrust that arises as a result of the pressure build-up in the opposite direction is generally absorbed by the spindles on the one hand and by means of an abutment on the housing side on the other. This bearing has proven itself in the delivery of lubricating fluids in the range of low delivery pressures, the lubricating effect of which enables axial bearings that are as simple as they are reliable.
Die Förderung nichtschmierender Fluide im Bereich höherer Förderdrucke beispielsweise Wasser, bringt für eine Schraubenspindelpume Erschwernisse mit sich, da zwischen den sich relativ zueinander bewegenden Pumpenteilen nur geringe Spaltweiten für das Fluid zur Verfügung stehen.The delivery of non-lubricating fluids in the area of higher delivery pressures, for example water, creates difficulties for a screw pump since only small gap widths are available for the fluid between the pump parts moving relative to one another.
Von besonderer Bedeutung sind für das Betreiben derartiger Schraubenspindelpumpen die Temperaturverhältnisse vor allem im Spindelbereich, weshalb Ziel dieser Erfindung die Vergleichmäßigung der Temperatur über die Länge des Pumpenrotors ist.The temperature conditions, particularly in the spindle area, are of particular importance for the operation of such screw pumps, which is why the aim of this invention is to make the temperature uniform over the length of the pump rotor.
Von besonderer Bedeutung sind für das Betreiben derartiger Schraubenspindelpumpen die Temperaturverhältnisse vor allem im Spindelbereich, weshalb Ziel dieser Erfindung die Vergleichmäßigung der Temperatur über die Länge des Pumpenrotors ist.The temperature conditions, particularly in the spindle area, are of particular importance for the operation of such screw pumps, which is why the aim of this invention is to make the temperature uniform over the length of the pump rotor.
Zur Lösung dieser Aufgabe führt, daß die Spindeln von einem rohrartigen Gehäuseeinsatz umgeben sind und dieser mit dem ihm umfangenden Pumpengehäuse wenigstens einen Ringraum begrenzt, der mit dem die Spindeln aufnehmenden Innenraum durch wenigstens einen Durchbruch verbunden ist. Dazu hat es sich als günstig erwiesen, den Ringraum saugseitig gegen den Innenraum abzudichten sowie an seinem druckseitigen Ende mit den radialen Durchbrüchen zu versehen.To achieve this object, the spindles are surrounded by a tubular housing insert and this, with the pump housing surrounding it, delimits at least one annular space which is connected to the interior receiving the spindles by at least one opening. For this purpose, it has proven to be advantageous to seal the annular space on the suction side against the interior and to provide the radial openings at its pressure end.
Nach einem weiteren Merkmal der Erfindung soll der Auslauf am saugseitigen Ende des Ringraumes vorgesehen sein. Außerdem ist bevorzugt ein saugseitiger Zulauf außerhalb des Gehäuseeinsatzes im radialen Bereich der Lagerung der Spindeln angeordnet.According to a further feature of the invention, the outlet should be provided at the suction-side end of the annular space. In addition, an inlet on the suction side is preferably arranged outside the housing insert in the radial region of the bearing of the spindles.
Dank dieser Maßgaben wird das Fluid durch die gesamte Länge des Ringraumes -- der somit einen Kühlmantel bestimmt -- geführt. Der erfindungsgemäße Gehäuseeinsatz ist problemlos zu fertigen und zu montieren. Auch kann er ohne weiteres innenseitig mit verschleißarmen Einlagen ausgestattet werden.Thanks to these measures, the fluid is guided through the entire length of the annular space, which thus defines a cooling jacket. The housing insert according to the invention is easy to manufacture and assemble. It can also be easily fitted with low-wear inserts on the inside.
Im Rahmen der Erfindung liegt es, an der innengelagerten Schraubenspindelpumpe zur Aufnahme des Axialschubes der Spindel/n Lagerkörper anzuordnen, welche das zapfenartige Spindelende bzw. einen Lagerzapfen aufnehmen sowie mit dem Druckram der Pumpe in Verbindung stehen. Zudem hat es sich als günstig erwiesen, den Lagerzapfen in eine Lagerbüchse zu legen und letztere ihrerseits in einer Ausnehmung des Pumpendeckels zu lagern.It is within the scope of the invention to arrange on the internally mounted screw pump for receiving the axial thrust of the spindle / n bearing bodies which receive the pin-like spindle end or a bearing pin and are connected to the pressure ram of the pump. In addition, it has proven to be advantageous to place the bearing journal in a bearing bush and to store the latter in turn in a recess in the pump cover.
Nach einem weiteren Merkmal der Erfindung begrenzt die freie Stirnseite der Lagerbüchse mit dem Boden der Ausnehmung des Pumpendeckels einen mit dem Innenraum der Schraubenspindelpumpe verbundenen dichten Spaltraum, der bevorzugt über eine radiale Leitung an eine Verlängerung des Innenraums angeschlossen ist. Außerdem umgibt den Profilauslauf der Dichtspindel eine Ausgleichsbüchse, die mit ihrem druckseitigen Ende an einer Schulter der Dichtspindel anschlägt. An diese Ausgleichsbüchse -- die mit ihrem saugseitigen Ende eine Steuerkante bildet -- schließt eine in der Lagerbüchse festliegende Schale aus verschleißarmem Werkstoff an, die vorteilhafterweise über die Stirnfläche des Lagerzapfens hinausragt; zwischen der Stirnfläche des Lagerzapfens und dem Boden der Lagerausnehmung ist ein mit dem Druckraum verbundener Stirnspalt erwünscht.According to a further feature of the invention, the free end face of the bearing bush with the bottom of the recess of the pump cover delimits a tight gap space connected to the interior of the screw pump, which is preferably connected to an extension of the interior via a radial line. In addition, the profile outlet of the sealing spindle is surrounded by a compensating bush, which strikes the shoulder of the sealing spindle with its pressure-side end. This compensating sleeve - which forms a control edge with its suction-side end - is adjoined by a shell made of low-wear material which is fixed in the bearing sleeve and which advantageously projects beyond the end face of the bearing journal; an end gap connected to the pressure chamber is desired between the end face of the bearing journal and the bottom of the bearing recess.
Die Stirnspalte der Lagerzapfen sollen vorteilhafterweise mittels jeweils wenigstens einer die Lagerbüchse durchsetzenden Leitung an eine Querleitung angeschlossen sein. Als günstig hat es sich erwiesen, von dem Boden der Lagerbüchse eine Bohrung ausgehen zu lassen, die an eine jenen Spaltraum durchsetzende Hülse als Teil der Leitung anschließt.The end gaps of the bearing journals should advantageously be connected to a transverse line by means of at least one line passing through the bearing bush. It has proven to be expedient to let a bore emanate from the bottom of the bearing bush, which bore connects to a sleeve penetrating that gap as part of the line.
Dank der beschriebenen Maßnahmen ist die Druckzuführung in den Lagerbüchsen abgedichtet, die Lagerbüchsen selbst aber sind radial beweglich.Thanks to the measures described, the pressure supply in the bearing bushes is sealed, but the bearing bushes themselves can be moved radially.
Erfindungsgemäß ist es möglich, die üblicherweise für schmierende Fluide konzipierte Schraubenspindelpumpe an einer funktionsentscheidenden Stelle -- insbesondere den hydrostatischen Axialschubausgleich beispielsweise auch bei Wasserförderung -- sicher zu beherrschen.According to the invention, it is possible to safely control the screw pump, which is usually designed for lubricating fluids, at a function-critical point - in particular the hydrostatic axial thrust compensation, for example also when pumping water.
Hierzu dient die spezifische Anordnung zylindrischer Lagerkörper oder Lagerbüchsen, in welche die Spindeln bis zu einem radialen Anschlag eintauchen. Die Lagerkörper oder -büchsen besitzen eine axiale Öffnung, die den Lagerraum -- in welchen der Spindelzapfen eingetaucht ist -- mit dem Druckraum der Pumpe verbindet. Der Anschluß der druckführenden Verbindung der Lagerhülse ist so gestaltet, daß der Fluiddruck ausschließlich auf dem Querschnitt des Spindelzapfens wirksam wird. So kann sich durch eine minimale Axialbewegung über die Spaltweite zwischen Spindel und axialem Bund ein Gleichgewicht zwischen Axialschub und hydraulischer Entlastung einpendeln. Die Einleitung des Pumpendruckes zum Ausgleich des Axialschubes ist so konzipiert, daß sich der Druck auf ausschließlich für den oben beschriebenen Zweck konzentrieren läßt.The specific arrangement of cylindrical bearing bodies or bearing bushes into which the spindles are immersed up to a radial stop serves this purpose. The bearing body or bushing has an axial opening that connects the storage space - in which the spindle pin is immersed - with the pressure chamber of the pump. The connection of the pressure-carrying connection of the bearing sleeve is designed so that the fluid pressure is effective only on the cross section of the spindle pin. A minimal axial movement across the gap between the spindle and the axial collar can balance the axial thrust and hydraulic relief. The introduction of the pump pressure to compensate for the axial thrust is designed so that the pressure can be concentrated on only for the purpose described above.
Damit dies alles gewährleistet ist, soll sich die Lagerhülse radial frei bewegen, d.h. sich an die radiale Bewegung der Spindel laufend anpassen können. Erfindungsgemäß wird durch eine kraftschlüssige Drehhemmung etwa in Form eines elastischen Ringelements sichergestellt, daß sich die Lagerbüchse nicht mitdreht, da ansonsten die notwendige Abdichtung zwischen Lagerkörper und der druckführenden Verbindung oder Leitung nicht gegeben wäre.In order for all this to be guaranteed, the bearing sleeve should move radially freely, ie be able to continuously adapt to the radial movement of the spindle. According to the invention, a non-positive rotation inhibition, for example in the form of an elastic ring element, ensures that the bearing bush does not rotate, since otherwise the necessary seal between the bearing body and the pressure-carrying connection or line would not be provided.
Weitere Vorteile, Merkmale und Einzelheiten der Erfindung ergeben sich aus der nachfolgenden Beschreibung eines bevorzugten Ausführungsbeispieles sowie anhand der Zeichnung; diese zeigt in
- Fig. 1:
- den Längsschnitt durch eine erfindungsgemäße Schraubenspindelpumpe;
- Fig. 2:
- einen zu Fig. 1 rechtwinklig gelegten Längsschnitt.
- Fig. 1:
- the longitudinal section through a screw pump according to the invention;
- Fig. 2:
- a longitudinal section perpendicular to Fig. 1.
Eine Schraubenspindelpumpe 10 weist im Innenraum 12 eines auf einen Pumpenfuß 11 geschraubten Pumpengehäuses 14 eine -- von zwei Dichte- oder Laufspindeln 16 flankierte -- Antriebsspindel 18 auf. Die Dicht- oder Laufspindeln 16 sind saugseitig in einem Pumpendeckel 20 gelagert, die Antriebsspindel 18 ist antriebsseitig an einen koaxialen Antriebswellenzapfen 22 angeschlossen.A
Der Antriebswellenzapfen 22 durchsetzt in einem Lagerdeckel 24 -- zwischen einem Labyrinthring 25 und einer Stützscheibe 26 mit nachgeordneter Schmierkammer 27 -- angeordnete Wälzlager 28. Jener Lagerdeckel 24 ist mittels Zylinderschrauben 29 sowie unter Zwischenschaltung einer Gleitringdichtung 30, 34 an einen antriebsseitigen Pumpendeckel 31 angeschlossen, wobei die Gleitringdichtung 30, 34 in einem Dichtungsraum 32 liegt. Daneben ist ein von verschleißarmen Schalen 35 umgebener sowie mit Drosselnuten versehener Ausgleichskolben 36 an einem Flansch 38 zu erkenne. Dieser ruht teilweise im Pumpendeckel 31 sowie teilweise im Pumpengehäuse 14, dessen Länge a etwa 270 mm beträgt.The
Auf die saugseitigen Lagerzapfen 17 der beiden Laufspindeln 16 ist jeweils eine Ausgleichsbuchse 40 der Länge n aufgeschrumpft, die an einen schulterartigen Absatz 42 der Laufspindel 16 anschlägt. Diese Ausgleichsbuchse 40 steht mit ihrem saugseitigen Ende einer Lagerausnehmung 44 eines Lagerkörpers bzw. einer Lagerbüchse 46 gegenüber und bildet dort eine Steuerkante zur Regelung des hydrostatischen Druckes. Der Steuerkante liegt hier der Rand einer in der Lagerausnehmung 44 sitzenden Schale 41 aus besonders verschleißarmem Werkstoff gegenüber.A
Die Länge t der Schale 41 ist größer als die freie Länge des Lagerzapfens 17 und bestimmt so die Weite eines zwischen der saugseitigen Stirnfläche 17s des Lagerzapfens 17 und dem Boden 45 der Lagerausnehmung 44 verbleibenden Stirnspalt 48. In diesen mündet eine axiale Zulaufbohrung 50 der Lagerbüchse 46; diese Zulaufbohrung 50 ist mittels einer -- eine Axialbohrung 52 aufweisenden -- Hülse 53 an einen Kanal 54 des saugseitigen Pumpendeckels 20 angeschlossen; die Kanäle 54 der Spindellager werden durch eine im Pumpendeckel 20 radial vorgesehene Sackbohrung 56 miteinander verbunden.The length t of the shell 41 is greater than the free length of the
Insbesondere Fig. 1 läßt erkennen, daß jene Hülse 53 einen Spaltraum 58 überbrückt, der zwischen der saugseitigen Stirn der Lagerbüchse 46 einerseits sowie dem Boden 60 einer diese aufnehmenden Sackausnehmung 58a des Pumpendeckels 20 entsteht. Dieser Spaltraum 58 ist über Radialbohrungen 59 an eine zylindrische Fortsetzung 13 des Innenraumes 12 des Pumpengehäuses 14 angeschlossen.In particular, FIG. 1 shows that said
Nahe dem Spaltraum 58 ist im Umfang der Lagerbüchse 46 ein O-Ring 62 als Dichtmittel zu erkennen - auch andere jeweils in Ringnuten vorgesehene O-Ringe sind mit 62 bezeichnet.Near the
Das Pumpengehäuse 14 ist so ausgestaltet, daß ein die Spindeln 16, 18 umgebender rohrartiger Gehäuseeinsatz 64 der Länge b von beispielsweise 190 mm beidends auf Gehäuserippen 66, 66s so aufliegt, daß zwischen Gehäuseeinsatz 64 und Pumpengehäuse 14 ein Ringraum 15 entsteht, der an der saugseitigen Gehäuserippe 66s zum Innenraum 12 hin mittels eines O-Rings 62 abgedichtet ist und im Bereich der anderen Gehäuserippe 66 Durchlässe 68 aufweist. Im übrigen ist der Gehäuseeinsatz 64 mit seiner druckseitigen Kante 64d zwischen Gehäuserippe 66 und Flansch 38 klemmend gehalten.The
Zwischen dem Gehäuseeinsatz 64 und den Spindeln 16, 18 sind Werkstoffeinsätze 70 aus verschleißfestem -- bevorzugt keramischem -- Material vorgesehen. Die Werkstoffeinsätze 70 sind an sich scheibenartig sowie mit aus Gründen der Übersichtlichkeit nicht gezeigten Aufnahmebohrungen für die sie durchsetzenden Spindeln 16, 18 versehen. Im Pumpengehäuse 14 sind mehrere dieser Werkstoffeinsätze 70 koaxial angeordnet.
Die Werkstoffeinsätze 70 werden mittels einer bei 71 angedeuteten Kunststoffschicht festgelegt, die durch Bohrungen 72 zwischen Gehäuseeinsatz 64 und Werkstoffeinsatz 70 eingebracht wird.The
Der beschriebene Ringraum 15 ist -- wie Fig. 1 erkennen läßt -- mittels einer achsparallelen Längsbohrung 74 im Pumpengehäuse 14 an die Sackbohrung 56 des Pumpendeckels 20 angeschlossen.The described
Insbesondere Fig. 2 läßt den Saugraumzulauf 76 sowie -- am Tiefsten des Ringraumes 15 -- den Auslauf 78 erkennen; zwischen beiden liegt jener Gehäuseeinsatz 64, so daß das Strömungsmittel zwischen dem Saugraumzulauf 76 und dem Auslauf 78 gezwungen ist, durch den Durchlaß 68 des Gehäuseeinsatzes 64 in den Ringraum 15 und über nahezu die gesamte Länge b des Gehäuseeinsatzes 64 zum Auslauf 78 zu fließen.In particular, FIG. 2 shows the
Claims (14)
- Screw rotor pump having a driving spindle arranged in the interior of a pump housing and at least one sealing spindle axially parallel thereto and an inlet and an outlet for a flow medium to be delivered by the spindles, characterised in that the spindles (16, 18) are surrounded by a tubular housing insert (64) which, together with the pump housing (14) surrounding it, defines at least one annular space (15) connected to the inner space (12) receiving the spindles by at least one opening (68).
- Screw rotor pump according to claim 1, characterised in that the annular space (15) is sealed off from the inner space (12) at the suction side and is provided at its delivery end with the radial openings (68).
- Screw rotor pump according to claim 1 or claim 2, characterised in that the outlet (78) is provided at the suction end of the annular space (15).
- Screw rotor pump according to one of claims 1 to 3, characterised in that a suction-side inlet (76) is arranged outside the housing insert (64) in the radial region of the bearing arrangement of the spindles (16, 18).
- Screw rotor pump according to one of claims 1 to 4, characterised in that the housing insert (64) is provided in its interior with at least one coating layer (70) of a wear-resistant material, the housing insert (64) possibly having recesses (72) for an adhesive substance (71).
- Screw rotor pump according to at least one of claims 1 to 5, characterised in that the coating layer consists of material discs (70) which are traversed by the spindles (16, 18), the housing insert (64) possibly having recesses (72) for an adhesive substance (71).
- Screw rotor pump with a cone-shaped spindle end according to at least one of claims 1 to 6, characterised in that bearing bodies (46) for receiving the axial thrust of the spindle/s (16) are arranged thereon, said bearing bodies receiving the cone-shaped spindle end or a bearing journal (17) and being connected to the annular space (15) of the screw rotor pump (10).
- Screw rotor pump with spindles supported on a pump cover according to at least one of claims 1 to 7, characterised in that the bearing recess (44) for the bearing journal (17) is provided as a bearing body in a bearing bush (46) and this bearing body rests in a recess (58a) in the pump cover (20), the free end face of the bearing bush (46), together with the base (60) of the recess (58a) in the pump cover (20), possibly defining a sealed gap (58) which is connected to the inner space (12) of the screw rotor pump (10).
- Screw rotor pump according to at least one of claims 1 to 8, characterised in that the free end face of the bearing body or the bearing bush (46) is connected to the inner space (12) of the screw rotor spindle (10), the free end face of the bearing bush (46), together with the base (60) of the recess (58a) in the pump cover (20), possibly defining a sealed gap (58) which is connected to the inner space (12) of the screw rotor pump (10) and/or at least one bore (59) connecting the gap (58) to an extension (13) of the inner space (12).
- Screw rotor pump according to at least one of claims 1 to 9, characterised in that a compensating bush (40) surrounds the bearing journal (17) and comes to rest via its delivery end against a shoulder (42) of the spindle (16).
- Screw rotor pump according to at least one of claims 1 to 10, characterised in that the compensating bush (40) forms a guiding edge with its suction end, the compensating bush (40) possibly lying opposite the bearing bush (46) or a wear-resistant shell (41) of the bearing bush via its guiding edge.
- Screw rotor pump according to at least one of claims 1 to 11, characterised in that an end gap (48) provided between the end face (17s) of the bearing journal (17) and the base (45) of the bearing recess (44) is connected to the annular space (15), the end gaps (48) of the bearing journals (17) preferably being connected to a transverse line (56) by means of at least one line (54) traversing the bearing bush (46).
- Screw rotor pump according to at least one of claims 1 to 12, characterised in that the pressure supply to the bearing bush (46) is sealed and/or a bore (50) departs from the base (60) of the bearing bush (46) and is connected as part of the line (54) to a sleeve (53) traversing the gap (58).
- Screw rotor pump according to at least one of claims 1 to 13, characterised in that the bearing bush (46) is arranged so that it is movable radially and/or that the bearing bush (46) is supported in a non-positive torsion-resistant manner by means of at least one flexible annular element (62).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| AT90110215T ATE92594T1 (en) | 1989-06-26 | 1990-05-30 | SCREW PUMP. |
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE3920900A DE3920900A1 (en) | 1989-06-26 | 1989-06-26 | SCREW PUMP |
| DE3920900 | 1989-06-26 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| EP0405160A1 EP0405160A1 (en) | 1991-01-02 |
| EP0405160B1 true EP0405160B1 (en) | 1993-08-04 |
Family
ID=6383606
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| EP90110215A Expired - Lifetime EP0405160B1 (en) | 1989-06-26 | 1990-05-30 | Screw rotor pump |
Country Status (3)
| Country | Link |
|---|---|
| EP (1) | EP0405160B1 (en) |
| AT (1) | ATE92594T1 (en) |
| DE (2) | DE3920900A1 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101208518B (en) * | 2005-06-02 | 2010-10-06 | 约翰·海因里希·波内曼有限公司 | Screw displacement pump |
Families Citing this family (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE19715224C2 (en) * | 1997-04-11 | 1999-04-15 | Leistritz Ag | Hydro rope elevator |
| CN103758758B (en) * | 2014-01-17 | 2015-11-25 | 西安交通大学 | A kind of AC servo direct-driving type electricity liquid pump |
| DE102014102390B3 (en) * | 2014-02-25 | 2015-03-26 | Leistritz Pumpen Gmbh | Screw Pump |
| DE102019118086A1 (en) * | 2019-07-04 | 2021-01-07 | Nidec Gpm Gmbh | Integrated screw spindle coolant pump |
| DE102020133555A1 (en) | 2020-12-15 | 2022-06-15 | Leistritz Pumpen Gmbh | screw pump |
| DE102021113724A1 (en) * | 2021-05-27 | 2022-12-01 | Jung & Co. Gerätebau GmbH | Single-flow screw pump |
| DE102021133112A1 (en) | 2021-12-14 | 2023-06-15 | Leistritz Pumpen Gmbh | screw pump |
Family Cites Families (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB578057A (en) * | 1944-04-05 | 1946-06-13 | Stothert & Pitt Ltd | Improvements in screw displacement pumps |
| US2592476A (en) * | 1948-02-07 | 1952-04-08 | Laval Steam Turbine Co | Series arrangement of positive and nonpositive screw pumps |
| US2873909A (en) * | 1954-10-26 | 1959-02-17 | Svenska Rotor Maskiner Ab | Rotary devices and casing structures therefor |
| FR1245458A (en) * | 1959-02-04 | 1960-11-04 | Imo Industri Ab | Helical gear pump |
| DE2520667C2 (en) * | 1975-05-09 | 1984-11-29 | Allweiler Ag, 7760 Radolfzell | Screw pump |
| DE3737358A1 (en) * | 1987-11-04 | 1989-05-18 | Allweiler Ag | Bearing housing for an inside-mounted screw pump, and method for its manufacture |
-
1989
- 1989-06-26 DE DE3920900A patent/DE3920900A1/en not_active Withdrawn
-
1990
- 1990-05-30 DE DE9090110215T patent/DE59002169D1/en not_active Expired - Fee Related
- 1990-05-30 AT AT90110215T patent/ATE92594T1/en not_active IP Right Cessation
- 1990-05-30 EP EP90110215A patent/EP0405160B1/en not_active Expired - Lifetime
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101208518B (en) * | 2005-06-02 | 2010-10-06 | 约翰·海因里希·波内曼有限公司 | Screw displacement pump |
Also Published As
| Publication number | Publication date |
|---|---|
| ATE92594T1 (en) | 1993-08-15 |
| EP0405160A1 (en) | 1991-01-02 |
| DE3920900A1 (en) | 1991-01-03 |
| DE59002169D1 (en) | 1993-09-09 |
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