EP0727581A1 - Screw rotor pump - Google Patents
Screw rotor pump Download PDFInfo
- Publication number
- EP0727581A1 EP0727581A1 EP96105318A EP96105318A EP0727581A1 EP 0727581 A1 EP0727581 A1 EP 0727581A1 EP 96105318 A EP96105318 A EP 96105318A EP 96105318 A EP96105318 A EP 96105318A EP 0727581 A1 EP0727581 A1 EP 0727581A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- pressure
- spindle
- length
- pulsation
- drive 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.)
- Granted
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Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
- F04C18/12—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
- F04C18/14—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
- F04C18/16—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw type
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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
- F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
- F04C15/0042—Systems for the equilibration of forces acting on the machines or pump
- F04C15/0049—Equalization of pressure pulses
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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
- F04C2/084—Toothed wheels
Definitions
- the invention relates to a screw pump with a drive spindle and at least one running spindle, which are mounted in a recess of a housing surrounding them between a suction chamber and a pressure chamber.
- Such a screw pump is described by way of example in DE-A 38 15 158.
- the type-typical pressure pulsation is overlaid with a forced inverse pressure pulsation, which can be achieved by periodically controlling a part of the flow on the pressure side of the conveyor screws.
- This method is made possible by a pressure-side diaphragm, which is designed with a drain to the suction side, which is periodically covered by a closure element depending on the rotational position of the drive spindle.
- wedge bevels tapering towards the suction space are incorporated into the receiving bores at the pressure-side end of the housing.
- EP-A 209 984 shows a screw pump mentioned at the outset, the drive spindle of which, with its projecting thread, engages in the thread formations of some running spindles and is said to form several tight chambers.
- at least one circumferential channel is provided around the periphery of the spindles, so that the last of the sealed chambers communicates at an outlet with it - shortly before it is released by the chamber - partially via the channel.
- the US-A-29 22 377 shows, as a defect in screw pumps, a high pressure, temperature and noise development due to the closed pockets arising at the discharge.
- a drive spindle is then described with a cross section tapering at an angle of, for example, 30 ° at the suction end in the region of an adapted desk surface of the housing. This arrangement is intended to prevent those closed pockets by producing a sealing edge over the entire length of the spindle (column 9, lines 17 to 39 op. Cit.).
- the tooth thickness of the drive spindle towards the profile runout should be reduced or the tooth gap of the spindle corresponding to this tooth thickness should be widened in the same direction.
- This pressure-side bevel causes a gradual and defined opening of the pressure-side chamber to take place at the appropriate time; This largely compensates for the increase in volume flow or pressure caused by closing the suction side. The initial pulsation is significantly reduced.
- the suction-side profile end can also be provided with such a flat conical surface, although the axial length of the latter conical surface should be less than the axial length of the pressure-side conical surface.
- a screw pump 10 has a drive spindle 14 of outside diameter d and two laterally arranged running spindles 16.
- the spindles 14, 16 are mounted in overlapping receiving bores 18 of the housing 12.
- the housing 12 is closed both on the pressure side and on the suction side to form a pressure chamber 20 and a suction chamber 22, each with a pump cover 25 or 24.
- the drive spindle 14, which is guided through the pressure-side pump cover 25, is provided with an axial thrust compensation piston 28 in the area of a through bore 26 and is additionally supported with a bearing 30 in a cover attachment 32. In the latter there is also a shaft seal 34.
- the interior 36 of the cap 32 is relieved of the delivery pressure; the liquid entering from the pressure chamber 20 is discharged via a relief channel 38 which opens into the suction chamber 22 via a connecting bore 40 in the housing 12.
- Fig. 2 shows that the drive spindle 14 - the profile length - is turned conically at their ends, wherein the length of the pressure-side taper 42 e, the length of the with that end face 44 by an amount i protruding suction cone 42 s with e 1 , the remaining cylinder length of the drive spindle 14 between the conical surfaces 43, 43 s with q, the pitch angle of the thread 15 of the drive spindle 14 - or the running spindle 16 - only partially indicated in FIG. 2 - with t and the pitch with s are.
- the pressure-side cone angle w or the suction-side cone angle w 1 is preferably 2 °.
- the length adjustment of the entire system is chosen so that a portion of the sealing lines shown in FIG. 3 is generated during part of the production period; this means an increase from Qvmax to Qvmin.
- the pulsation pattern is thus changed by attaching the described conical surface 43 to the pressure-side spindle end, which leads to a decrease in Qv and Q kom .
- the extension of the cross-sectionally inclined conical surface 43 has the effect that, on the one hand, the pressure side opens earlier, and on the other hand, the cross-sections become continuously larger during opening. It may be sufficient to provide the pressure side with the cone 42 and to leave the spindle end on the suction side cylindrical.
- the operating system for the three-spindle screw pump 10 shown can be described as follows:
- the ratio of length to slope - i.e. thus a / s - represents an analog quantity for the geometric realization; the greater this ratio, the smaller the pressure increase per unit length.
- the pre-factor x is a measure of the pre-compression, which, depending on the profile, only occurs for values above 0.1 - 0.15.
- the pressure-side cone 42 must be matched to that dimension x - that is, to the pre-compression achieved.
- the length e is chosen such that for the normal case
- the cone 42 s on the suction side generally allows the closing characteristic to be adapted, as is shown at A 'in FIG. 2.
- This cone 42 s must be precisely matched to the pressure-side cone 42 on the basis of a defined length ratio a / s.
- the length e 1 of the cone 42 s is expediently chosen to be smaller than the length e of the other cone 42.
- the length e of the pressure-side cone 42 must be made smaller overall.
- the tooth thickness b of the thread 15 of the drive spindle 14 is reduced at the profile runout.
- the tooth gap of the spindle 16 can also be widened.
- the design change of the tooth thickness b or the tooth gaps towards the profile runout is to be carried out so that the pre-opening can take place early enough; the length of the change x 1 according to FIG. 4 in the profile must be clear in relation to the spindle pitch s.
- the reduction in tooth thickness or the widening of the tooth gap must have a small gradient y: x 1 .
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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)
- Reciprocating Pumps (AREA)
- Pharmaceuticals Containing Other Organic And Inorganic Compounds (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
- Supercharger (AREA)
Abstract
Description
Die Erfindung betrifft eine Schraubenspindelpumpe mit einer Antriebsspindel und wenigstens einer Laufspindel, die in einer Ausnehmung eines sie umgebenden Gehäuses zwischen einem Saugraum und einem Druckraum gelagert sind.The invention relates to a screw pump with a drive spindle and at least one running spindle, which are mounted in a recess of a housing surrounding them between a suction chamber and a pressure chamber.
Eine solche Schraubenspindelpumpe wird beispielhaft in der DE-A 38 15 158 beschrieben. Bei einem dort offenbarten Verfahren zur Verringerung der Druckpulsation wird die arttypische Druckpulsation mit einer erzwungenen inversen Druckpulsation überlagert, welche durch periodisches Absteuern eines Teiles des Förderstromes auf der Druckseite der Förderschrauben erzielbar ist. Dieses Verfahren wird durch eine druckseitige Blende ermöglicht, die mit einem Abfluß zur Saugseite hin ausgebildet ist, welche periodisch abhängig von der Drehstellung der Antriebsspindel mittels eines Verschlußorganes abgedeckt wird. In dieser Druckschrift wird auch erörtert, daß in die Aufnahmebohrungen am druckseitigen Ende des Gehäuses sich zum Saugraum hin verjüngende Keilschrägen eingearbeitet sind.Such a screw pump is described by way of example in DE-A 38 15 158. In a method disclosed there for reducing the pressure pulsation, the type-typical pressure pulsation is overlaid with a forced inverse pressure pulsation, which can be achieved by periodically controlling a part of the flow on the pressure side of the conveyor screws. This method is made possible by a pressure-side diaphragm, which is designed with a drain to the suction side, which is periodically covered by a closure element depending on the rotational position of the drive spindle. In this document it is also discussed that wedge bevels tapering towards the suction space are incorporated into the receiving bores at the pressure-side end of the housing.
Der EP-A 209 984 kann eine eingangs erwähnte Schraubenspindelpumpe entnommen werden, deren Antriebsspindel mit ihrem auskragenden Gewinde in Gewindeeinformungen einiger Laufspindeln eingreift und dabei mehrere dichte Kammern bilden soll. Außerdem ist zumindest ein in Umfangsrichtung verlaufender Kanal um die Peripherie der Laufspindeln vorgesehen, so daß die letzte der dichten Kammern an einem Auslaß mit diesem -- kurz vor dessen Freigabe durch die Kammer -- teilweise über den Kanal kommuniziert.EP-A 209 984 shows a screw pump mentioned at the outset, the drive spindle of which, with its projecting thread, engages in the thread formations of some running spindles and is said to form several tight chambers. In addition, at least one circumferential channel is provided around the periphery of the spindles, so that the last of the sealed chambers communicates at an outlet with it - shortly before it is released by the chamber - partially via the channel.
Die US-A-29 22 377 zeigt als Fehler an Schraubenspindelpumpen eine hohe Druck-, Temperatur- und Lärmentwicklung infolge am Austrag entstehender geschlossener Taschen auf. Beschrieben wird dann eine Antriebsspindel mit sich in einem Winkel von beispielsweise 30° verjüngendem Querschnitt am Saugende im Bereich einer angepaßten Pultfläche des Gehäuses. Diese Anordnung soll jene geschlossenen Taschen durch Herstellung einer Dichtkante über die gesamte Spindellänge verhindern (Spalte 9, Zeilen 17 bis 39 aaO.).The US-A-29 22 377 shows, as a defect in screw pumps, a high pressure, temperature and noise development due to the closed pockets arising at the discharge. A drive spindle is then described with a cross section tapering at an angle of, for example, 30 ° at the suction end in the region of an adapted desk surface of the housing. This arrangement is intended to prevent those closed pockets by producing a sealing edge over the entire length of the spindle (column 9, lines 17 to 39 op. Cit.).
In Kenntnis dieses Standes der Technik hat sich der Erfinder das Ziel gesetzt, eine Schraubenspindelpumpe der eingangs genannten Art dahingehend zu verbessern, daß die Druckpulsation ohne zusätzliche Maschinenteile weitergehend wirksam gedämpft wird.Knowing this state of the art, the inventor has set himself the goal of improving a screw pump of the type mentioned at the outset in such a way that the pressure pulsation is effectively damped without additional machine parts.
Zur Lösung dieser Aufgabe führt eine Schraubenspindelpumpe nach der Lehre des Patentanspruches 1.To solve this problem, a screw pump leads to the teaching of claim 1.
Im Rahmen der Erfindung soll die Zahndicke der Antriebsspindel zum Profilauslauf hin verringert bzw. die mit dieser Zahndicke korrespondierende Zahnlücke der Laufspindel in gleicher Richtung verbreitert sein.In the context of the invention, the tooth thickness of the drive spindle towards the profile runout should be reduced or the tooth gap of the spindle corresponding to this tooth thickness should be widened in the same direction.
Diese druckseitige Anschrägung bewirkt, daß zum geeigneten Zeitpunkt ein allmähliches und definiertes Öffnen der druckseitigen Kammer erfolgt; damit kann der durch das Schließen der Saugseite entstehende Volumenstrom- bzw. Druckanstieg größtenteils ausgeglichen werden. Die Ausgangspulsation wird deutlich verringert.This pressure-side bevel causes a gradual and defined opening of the pressure-side chamber to take place at the appropriate time; This largely compensates for the increase in volume flow or pressure caused by closing the suction side. The initial pulsation is significantly reduced.
Nach einem weiteren Merkmal der Erfindung kann auch das saugseitige Profilende mit einer derartigen flachen Konusfläche versehen sein, wobei allerdings die axiale Länge der letztgenannten Konusfläche geringer sein soll als die axiale Länge der druckseitigen Konusfläche.According to a further feature of the invention, the suction-side profile end can also be provided with such a flat conical surface, although the axial length of the latter conical surface should be less than the axial length of the pressure-side conical surface.
Somit wird erreicht, daß durch ein gezieltes Abstimmen von Systemwirklänge und druckseitigem -- gegebenenfalls zusätzlich saugseitigem -- Konus die Pulsation verringert wird.It is thus achieved that the pulsation is reduced by a specific coordination of system effective lengths and pressure-side - possibly additionally suction-side - cone.
Weitere Vorteile, Merkmale und Einzelheiten der Erfindung ergeben sich aus der nachfolgenden Beschreibung bevorzugter Ausführungsbeispiele sowie anhand der Zeichnung; diese zeigt in:
- Fig. 1:
- einen Längsschnitt durch eine Schraubenspindelpumpe;
- Fig. 2:
- einen vergrößerten Teilschnitt durch die Schraubenspindelpumpe;
- Fig. 3:
- ein Diagramm zur Druckpulsation bzw. Volumenstrompulsation der Schraubenspindelpumpe;
- Fig. 4:
- eine Schnittskizze zur Zahndickendimensionierung.
- Fig. 1:
- a longitudinal section through a screw pump;
- Fig. 2:
- an enlarged partial section through the screw pump;
- Fig. 3:
- a diagram of the pressure pulsation or volume flow pulsation of the screw pump;
- Fig. 4:
- a sectional sketch for dimensioning the tooth thickness.
Eine Schraubenspindelpumpe 10 weist in einem Gehäuse 12 eine Antriebsspindel 14 des Außendurchmessers d sowie zwei seitlich angeordnete Laufspindeln 16 auf. Die Spindeln 14, 16 sind in sich überschneidenden Aufnahmebohrungen 18 des Gehäuses 12 gelagert.In a
Das Gehäuse 12 ist sowohl druckseitig als auch saugseitig unter Bildung eines Druckraums 20 und eines Saugraums 22 jeweils mit einem Pumpendeckel 25 bzw. 24 verschlossen. Die durch den druckseitigen Pumpendeckel 25 geführte Antriebsspindel 14 ist im Bereich einer Durchführungsbohrung 26 mit einem Axialschubausgleichkolben 28 versehen sowie mit einem Lager 30 in einem Deckelaufsatz 32 zusätzlich abgestützt. In letzterem findet sich auch eine Wellenabdichtung 34.The
Der Innenraum 36 des Deckel aufsatzes 32 ist vom Förderdruck entlastet; die vom Druckraum 20 eintretende Flüssigkeit wird über einen Entlastungskanal 38 abgeführt, der über eine Verbindungsbohrung 40 des Gehäuses 12 in den Saugraum 22 einmündet.The
Fig. 2 macht deutlich, daß die Antriebsspindel 14 -- der Profillänge -- an ihren Enden konisch abgedreht ist, wobei die Länge des druckseitigen Konus 42 mit e, die Länge des mit jener Stirnfläche 44 um ein Maß i überstehenden saugseitigen Konus 42s mit e1, die zwischen den Konusflächen 43, 43s verbleibende Zylinderlänge der Antriebsspindel 14 mit q, der Steigungswinkel des in Fig. 2 nur teilweise angedeuteten Gewindeganges 15 der Antriebsspindel 14 -- oder der Laufspindel 16 -- mit t sowie die Steigung mit s bezeichnet sind. Der druckseitige Konuswinkel w bzw. der saugseitige Konuswinkel w1 liegt bevorzugt bei 2°.Fig. 2 shows that the drive spindle 14 - the profile length - is turned conically at their ends, wherein the length of the pressure-side taper 42 e, the length of the with that end face 44 by an amount i protruding
In Fig. 3 ist graphisch die Längsoptimierung durch eine erfindungsgemäße Vorkompression dargestellt, wobei die dort verwendeten Buchstaben die folgenden Bedeutungen haben:
- A:
- Ausgangspulsation;
- B:
- Pulsation bei Nutzung des Vorkompressionseffektes;
- Qv:
- Verlustvolumenstrom;
- Qkom:
- Kompressionsvolumenstrom.
- A:
- Initial pulsation;
- B:
- Pulsation when using the pre-compression effect;
- Qv:
- Loss volume flow;
- Q com :
- Compression volume flow.
Die Längenabstimmung des gesamten Systems wird so gewählt, daß während eines Teils der Förderperiode ein in Fig. 3 wiedergegebenes Mehr an Dichtlinien erzeugt wird; dies bedeutet, einen Anstieg von Qvmax auf Qvmin. Durch gezieltes Verändern der Dichtgüte über den beschriebenen Konus 42 wird insbesondere auf der Druckseite das "harte" Öffnen aufgrund der Spindelgeometrie vermieden.The length adjustment of the entire system is chosen so that a portion of the sealing lines shown in FIG. 3 is generated during part of the production period; this means an increase from Qvmax to Qvmin. By deliberately changing the sealing quality via the described
Ausgehend von der Ausgangspulsation wird somit durch das Anbringen der beschriebenen Konusfläche 43 am druckseitigen Spindelende das Pulsationsbild geändert, was zu einem Kleinerwerden von Qv und Qkom führt. Die Verlängerung der querschnittlich schrägen Konusfläche 43 bewirkt, daß einerseits die Druckseite früher öffnet, anderseits die Querschnitte während des Öffnens kontinuierlich größer werden. So kann es ausreichen, die Druckseite mit dem Konus 42 zu versehen und das saugseitige Spindelende zylindrisch zu belassen.Starting from the initial pulsation, the pulsation pattern is thus changed by attaching the described
Für die dargestellte dreispindelige Schraubenspindelpumpe 10 kann das Wirksystem folgendermaßen beschrieben werden:The operating system for the three-
Unter Zugrundelegung einer bestimmten Kammerzahl n, welche ein Maß für den pumpeninternen Druckaufbau ist, stellt das Verhältnis von Länge zu Steigung --, d.h. also a/s -- eine analoge Größe für die geometrische Realisierung dar; je größer dieses Verhältnis ist, umso kleiner wird der Druckanstieg je Längeneinheit.On the basis of a certain number of chambers n, which is a measure of the pump's internal pressure build-up, the ratio of length to slope - i.e. thus a / s - represents an analog quantity for the geometric realization; the greater this ratio, the smaller the pressure increase per unit length.
Für die Anwendung des Vorkompressionsverfahrens sind bei der Längenabstimmung folgende Voraussetzungen zu erfüllen:
- x
ein Vorfaktor mit 0,15 < x < 0,4 ist, und - n die Anzahl der im Mittel wirkenden Kammern beschreibt.
- x is a prefactor with 0.15 <x <0.4, and
- n describes the number of chambers acting on average.
Der Vorfaktor x ist ein Maß für die Vorkompression, die im übrigen profilabhängig erst für Werte oberhalb von 0,1 - 0,15 auftritt.The pre-factor x is a measure of the pre-compression, which, depending on the profile, only occurs for values above 0.1 - 0.15.
Zu beachten ist, daß sich die nachstehenden Angaben auf das besonders vorteilhafte erfindungsgemäße Anschrägen der Antriebsspindel 14 beziehen.It should be noted that the following information relates to the particularly advantageous chamfering of the
Bei konstantem Winkel w (0 < w < 3°) muß der druckseitige Konus 42 auf jenes Maß x -- also auf die erzielte Vorkompression -- abgestimmt werden. So wird beispielsweise für einen Winkel w von etwa 2° die Länge e derart gewählt, daß für den NormalfallAt a constant angle w (0 <w <3 °), the pressure-
e ≤ x . s gilt; hier tritt etwa bei x = 0,25; n = 3; s = 80 mm, d.h. einem a = 2,25 und einem druckseitigen Konus 42 einer Länge e von 20 mm eine nur sehr kleine Restpulsation auf.e ≤ x. s applies; here occurs approximately at x = 0.25; n = 3; s = 80 mm, ie an a = 2.25 and a pressure-
Der Konus 42s auf der Saugseite erlaubt ganz allgemein die Anpassung der Schließcharakteristik, wie es bei A' in Fig. 2 dargestellt ist. Dieser Konus 42s muß unter Zugrundelegung eines definierten Längenverhältnisses a/s auf den druckseitigen Konus 42 genau abgestimmt sein. So ist zweckmäßigerweise die Länge e1 des Konus 42s kleiner zu wählen als die Länge e des anderen Konus 42. Ferner ist bei unverändertem Maß des Spindelpakets 14, 16 die Länge e des druckseitigen Konus 42 insgesamt kleiner zu gestalten.The
Eine sorgfältige Abstimmung der Gesamtgeometrie führt zu einer wirksamen Pulsationsverringerung in einem weiten Druckbereich von 10 bis 80 bar sowie im und Viskositätsbereich von 20 bis 200 mm2/s.Careful coordination of the overall geometry leads to effective pulsation reduction in a wide pressure range from 10 to 80 bar and in the and viscosity range from 20 to 200 mm 2 / s.
In jedem Falle wird ohne zusätzliche Maschinenteile eine deutlich verringerte Pulsation erreicht.In any case, a significantly reduced pulsation is achieved without additional machine parts.
Bei einem nicht dargestellten Ausführungsbeispiel wird die Zahndicke b des Gewindeganges 15 der Antriebsspindel 14 an deren Profilauslauf vermindert. Auch kann die Zahnlücke der Laufspindel 16 verbreitert werden.In an embodiment not shown, the tooth thickness b of the
Die konstruktive Änderung der Zahndicke b bzw. der Zahnlücken zum Profilauslauf hin ist so vorzunehmen, daß die Voröffnung früh genug stattfinden kann; die Länge der Änderung x1 gemäß Fig. 4 im Profil muß im Verhältnis zur Spindelsteigung s deutlich sein. Zum anderen muß die Verminderung der Zahndicke bzw. die Verbreiterung der Zahnlücke einen geringen Gradienten y: x1 aufweisen.The design change of the tooth thickness b or the tooth gaps towards the profile runout is to be carried out so that the pre-opening can take place early enough; the length of the change x 1 according to FIG. 4 in the profile must be clear in relation to the spindle pitch s. On the other hand, the reduction in tooth thickness or the widening of the tooth gap must have a small gradient y: x 1 .
Claims (2)
dadurch gekennzeichnet,
daß die Zahndicke (b) der Antriebsspindel (14) zu ihrem Profilauslauf hin vermindert ist.Screw pump with a drive spindle and at least one running spindle, which are mounted in a recess of a housing surrounding them between a suction chamber and a pressure chamber,
characterized,
that the tooth thickness (b) of the drive spindle (14) is reduced towards its profile runout.
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE4007273 | 1990-03-08 | ||
DE4007273 | 1990-03-08 | ||
EP91710004A EP0451085B1 (en) | 1990-03-08 | 1991-03-07 | Screw rotor pump |
Related Parent Applications (2)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP91710004A Division EP0451085B1 (en) | 1990-03-08 | 1991-03-07 | Screw rotor pump |
EP91710004.2 Division | 1991-03-07 |
Publications (2)
Publication Number | Publication Date |
---|---|
EP0727581A1 true EP0727581A1 (en) | 1996-08-21 |
EP0727581B1 EP0727581B1 (en) | 1999-02-10 |
Family
ID=6401666
Family Applications (2)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP96105318A Expired - Lifetime EP0727581B1 (en) | 1990-03-08 | 1991-03-07 | Screw rotor pump |
EP91710004A Expired - Lifetime EP0451085B1 (en) | 1990-03-08 | 1991-03-07 | Screw rotor pump |
Family Applications After (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP91710004A Expired - Lifetime EP0451085B1 (en) | 1990-03-08 | 1991-03-07 | Screw rotor pump |
Country Status (6)
Country | Link |
---|---|
US (1) | US5123821A (en) |
EP (2) | EP0727581B1 (en) |
JP (1) | JP3036874B2 (en) |
KR (1) | KR0177815B1 (en) |
AT (2) | ATE169721T1 (en) |
BR (1) | BR9100993A (en) |
Families Citing this family (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FI104440B (en) * | 1995-06-22 | 2000-01-31 | Kone Corp | Screw pump and screw pump screw |
US6623262B1 (en) | 2001-02-09 | 2003-09-23 | Imd Industries, Inc. | Method of reducing system pressure pulsation for positive displacement pumps |
GB0226529D0 (en) * | 2002-11-14 | 2002-12-18 | Dana Automotive Ltd | Pump |
US8096288B2 (en) * | 2008-10-07 | 2012-01-17 | Eaton Corporation | High efficiency supercharger outlet |
DE102017210767B4 (en) * | 2017-06-27 | 2019-10-17 | Continental Automotive Gmbh | Screw pump, fuel delivery unit and fuel delivery unit |
Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2652192A (en) * | 1947-06-13 | 1953-09-15 | Curtiss Wright Corp | Compound-lead screw compressor or fluid motor |
Family Cites Families (12)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2952216A (en) * | 1956-03-13 | 1960-09-13 | Wildhaber Ernest | Rotary screw unit for displacing fluid |
US2922377A (en) * | 1957-09-26 | 1960-01-26 | Joseph E Whitfield | Multiple arc generated rotors having diagonally directed fluid discharge flow |
CH390690A (en) * | 1959-02-23 | 1965-04-15 | Imo Industri Ab | Screw pump |
FR1243471A (en) * | 1959-08-31 | 1960-10-14 | Improvements to rotors for pumps, motors, compressors, fans, meters and other similar devices | |
US3103894A (en) * | 1960-02-18 | 1963-09-17 | Laval Turbine | Screw pump |
DE2033201C3 (en) * | 1970-07-04 | 1979-02-01 | Allweiler Ag | Screw motor or pump |
SE383774B (en) * | 1975-04-02 | 1976-03-29 | Imo Industri Ab | SCREW PUMP |
JPS5238615A (en) * | 1975-09-22 | 1977-03-25 | Mayekawa Mfg Co Ltd | Screw compressor |
JPS5936116B2 (en) * | 1976-08-07 | 1984-09-01 | 株式会社荏原製作所 | fluid machinery |
FR2538463B1 (en) * | 1982-12-23 | 1985-06-21 | Dba | VOLUMETRIC CONICAL SCREW MACHINE |
JPS61294178A (en) * | 1985-06-24 | 1986-12-24 | Kawasaki Heavy Ind Ltd | Screw pump |
DE3815158A1 (en) * | 1988-05-04 | 1989-11-16 | Allweiler Ag | Method for reducing the pressure pulsation of a positive-displacement pump, in particular a screw pump, and a screw pump designed according to this method |
-
1990
- 1990-11-26 US US07/617,678 patent/US5123821A/en not_active Expired - Lifetime
-
1991
- 1991-03-07 AT AT91710004T patent/ATE169721T1/en not_active IP Right Cessation
- 1991-03-07 EP EP96105318A patent/EP0727581B1/en not_active Expired - Lifetime
- 1991-03-07 AT AT96105318T patent/ATE176717T1/en not_active IP Right Cessation
- 1991-03-07 EP EP91710004A patent/EP0451085B1/en not_active Expired - Lifetime
- 1991-03-08 KR KR1019910003767A patent/KR0177815B1/en not_active IP Right Cessation
- 1991-03-08 JP JP3069138A patent/JP3036874B2/en not_active Expired - Lifetime
- 1991-03-08 BR BR919100993A patent/BR9100993A/en not_active IP Right Cessation
Patent Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2652192A (en) * | 1947-06-13 | 1953-09-15 | Curtiss Wright Corp | Compound-lead screw compressor or fluid motor |
Also Published As
Publication number | Publication date |
---|---|
JP3036874B2 (en) | 2000-04-24 |
EP0451085B1 (en) | 1998-08-12 |
JPH05231341A (en) | 1993-09-07 |
EP0727581B1 (en) | 1999-02-10 |
EP0451085A3 (en) | 1992-07-08 |
KR910017081A (en) | 1991-11-05 |
KR0177815B1 (en) | 1999-04-15 |
BR9100993A (en) | 1991-11-05 |
US5123821A (en) | 1992-06-23 |
EP0451085A2 (en) | 1991-10-09 |
ATE176717T1 (en) | 1999-02-15 |
ATE169721T1 (en) | 1998-08-15 |
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