EP0727581A1 - Screw rotor pump - Google Patents

Screw rotor pump Download PDF

Info

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
Application number
EP96105318A
Other languages
German (de)
French (fr)
Other versions
EP0727581B1 (en
Inventor
Rolf Dipl.-Ing. Quast
Klaus Dipl.-Ing. Willibald
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Allweiler GmbH
Original Assignee
Allweiler AG
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Family has litigation
First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=6401666&utm_source=***_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=EP0727581(A1) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Application filed by Allweiler AG filed Critical Allweiler AG
Publication of EP0727581A1 publication Critical patent/EP0727581A1/en
Application granted granted Critical
Publication of EP0727581B1 publication Critical patent/EP0727581B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

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
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C18/12—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C18/14—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
    • F04C18/16—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • 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
    • 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 .

Landscapes

  • 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

The screw spindle pump has a drive spindle and at least one running spindle. They are mounted in the recess of a housing between a suction chamber and a pressure chamber. The pressure-side profile run-out of the spindle (14) is conically turned at the OD (d) and the angle of inclination (w) of the conical surface (43) lies below 10 deg.

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.
Further advantages, features and details of the invention result from the following description of preferred exemplary embodiments and from the drawing; this shows in:
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 housing 12, 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.

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 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.

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 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 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 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 °.

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.
3 shows the longitudinal optimization by means of a pre-compression according to the invention, the letters used there having the following meanings:
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 cone 42, the "hard" opening due to the spindle geometry is avoided, in particular on the pressure side.

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 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.

Für die dargestellte dreispindelige Schraubenspindelpumpe 10 kann das Wirksystem folgendermaßen beschrieben werden:The operating system for the three-spindle screw pump 10 shown can be described as follows:

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: a ̲ = 1 + (2 . n - 1) . x mit nE N, d.h. 1,2, ....

Figure imgb0001
wobei

  • x ein Vorfaktor mit 0,15 < x < 0,4 ist, und
  • n die Anzahl der im Mittel wirkenden Kammern beschreibt.
When using the pre-compression procedure, the following requirements must be met when adjusting the length: a ̲ = 1 + (2. N - 1). x with nE N, ie 1.2, ....
Figure imgb0001
 in which
  • 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 drive spindle 14 according to the invention.

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-side cone 42 must be matched to that dimension x - that is, to the pre-compression achieved. For example, for an angle w of approximately 2 °, the length e is chosen such that for the normal case

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-side cone 42 with a length e of 20 mm, only a very small residual pulsation.

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 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. Thus, the length e 1 of the cone 42 s is expediently chosen to be smaller than the length e of the other cone 42. Furthermore, with the dimensions of the spindle package 14, 16 unchanged, the length e of the pressure-side cone 42 must be made smaller overall.

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 thread 15 of the drive spindle 14 is reduced at the profile runout. The tooth gap of the spindle 16 can also be widened.

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)

Schraubenspindelpumpe mit einer Antriebsspindel und wenigstens einer Laufspindel, die in einer Ausnehmung eines sie umgebenden Gehäuses zwischen einem Saugraum und einem Druckraum gelagert sind,
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. Schraubenspindelpumpe nach Anspruch 1, dadurch gekennzeichnet, daß die mit der Zahndicke (b) der Antriebsspindel (14) korrespondierende Zahnlücke der Laufspindel (16) zu ihrem Profilauslauf hin verbreitert ist.Screw pump according to claim 1, characterized in that the tooth gap of the spindle (16) corresponding to the tooth thickness (b) of the drive spindle (14) is widened towards its profile runout.
EP96105318A 1990-03-08 1991-03-07 Screw rotor pump Expired - Lifetime EP0727581B1 (en)

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)

* Cited by examiner, † Cited by third party
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)

* Cited by examiner, † Cited by third party
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)

* Cited by examiner, † Cited by third party
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

Patent Citations (1)

* Cited by examiner, † Cited by third party
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

Similar Documents

Publication Publication Date Title
EP0256221B1 (en) Sealing device for a rod
DE19604132C2 (en) High pressure plunger pump, preferably for working pressures above 2,000 bar
DE69202399T2 (en) Flow machine in spiral construction.
DE102019100158A1 (en) Gerotor pump with radial gap compensation
EP0563661A1 (en) Internal gear pump with radially movable sealing elements for radial compensation
DE3429935C2 (en) Direct operated vane pump
DE69015795T2 (en) Vane displacement pump.
DE1653801A1 (en) Capsule pump
EP0727581A1 (en) Screw rotor pump
DE4107315C2 (en)
EP1219841B1 (en) Slide bearing,especially for a gear pump
DE7625526U1 (en) ROTOR DISPENSER MACHINE
WO1999054627A1 (en) Positive displacement machine
DE2737659C2 (en) Vane vacuum pump
EP1276992B1 (en) Gear-wheel pump, in particular for a high-pressure fuel pump
DE69606803T3 (en) Screw pump and screw rotor for a screw pump
DE8514497U1 (en) High pressure piston pump
DE3641682A1 (en) Seal for a ball screw
DE4115642C2 (en)
EP0628725A2 (en) Gear pump
DE3145494A1 (en) Device for guiding the piston of a working cylinder
DE9006233U1 (en) Rotary piston compressor
EP1722104B1 (en) Rotor pair for a screw compressor
DE2336147A1 (en) DEVICE FOR HYDRAULIC PISTON SEALING IN HIGH PRESSURE PISTON PUMPS
DE2240423A1 (en) CONVEYOR DEVICE, IN PARTICULAR CONVEYOR PUMP

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AC Divisional application: reference to earlier application

Ref document number: 451085

Country of ref document: EP

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AT GB IT SE

RBV Designated contracting states (corrected)

Designated state(s): AT GB IT SE

17P Request for examination filed

Effective date: 19970121

17Q First examination report despatched

Effective date: 19980112

GRAG Despatch of communication of intention to grant

Free format text: ORIGINAL CODE: EPIDOS AGRA

GRAG Despatch of communication of intention to grant

Free format text: ORIGINAL CODE: EPIDOS AGRA

GRAH Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOS IGRA

GRAH Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOS IGRA

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AC Divisional application: reference to earlier application

Ref document number: 451085

Country of ref document: EP

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AT GB IT SE

REF Corresponds to:

Ref document number: 176717

Country of ref document: AT

Date of ref document: 19990215

Kind code of ref document: T

ITF It: translation for a ep patent filed

Owner name: DE DOMINICIS & MAYER S.R.L.

GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)

Effective date: 19990512

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed
PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20000222

Year of fee payment: 10

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: AT

Payment date: 20000320

Year of fee payment: 10

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: SE

Payment date: 20000323

Year of fee payment: 10

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20010307

Ref country code: AT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20010307

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20010308

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20010307

EUG Se: european patent has lapsed

Ref document number: 96105318.8

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES;WARNING: LAPSES OF ITALIAN PATENTS WITH EFFECTIVE DATE BEFORE 2007 MAY HAVE OCCURRED AT ANY TIME BEFORE 2007. THE CORRECT EFFECTIVE DATE MAY BE DIFFERENT FROM THE ONE RECORDED.

Effective date: 20050307