EP1538338A1 - Radial pump - Google Patents

Radial pump Download PDF

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Publication number
EP1538338A1
EP1538338A1 EP03450273A EP03450273A EP1538338A1 EP 1538338 A1 EP1538338 A1 EP 1538338A1 EP 03450273 A EP03450273 A EP 03450273A EP 03450273 A EP03450273 A EP 03450273A EP 1538338 A1 EP1538338 A1 EP 1538338A1
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EP
European Patent Office
Prior art keywords
cover ring
impeller
housing
radial pump
guide surface
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
EP03450273A
Other languages
German (de)
French (fr)
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EP1538338B1 (en
Inventor
Alfred Ing. Götschhofer
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.)
TCG Unitech Systemtechnik GmbH
Original Assignee
TCG Unitech Systemtechnik GmbH
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
Application filed by TCG Unitech Systemtechnik GmbH filed Critical TCG Unitech Systemtechnik GmbH
Priority to DE50303864T priority Critical patent/DE50303864D1/en
Priority to EP03450273A priority patent/EP1538338B1/en
Priority to AT03450273T priority patent/ATE330127T1/en
Priority to AT04450193T priority patent/ATE346240T1/en
Priority to DE502004002076T priority patent/DE502004002076D1/en
Priority to EP20040450193 priority patent/EP1538339B1/en
Publication of EP1538338A1 publication Critical patent/EP1538338A1/en
Application granted granted Critical
Publication of EP1538338B1 publication Critical patent/EP1538338B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/08—Sealings
    • F04D29/16—Sealings between pressure and suction sides
    • F04D29/165—Sealings between pressure and suction sides especially adapted for liquid pumps
    • F04D29/167—Sealings between pressure and suction sides especially adapted for liquid pumps of a centrifugal flow wheel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D15/00—Control, e.g. regulation, of pumps, pumping installations or systems
    • F04D15/0027—Varying behaviour or the very pump
    • F04D15/0033—By-passing by increasing clearance between impeller and its casing

Definitions

  • the invention relates to a radial pump with a housing in which a is rotatably supported by a shaft driven impeller, with a on the Suction side of the impeller in the housing axially in the direction of the impeller axis between two end positions slidably mounted cover ring, wherein by moving the Cover ring from a limited by a housing stop first end position a gap formed between the impeller and the housing can be released.
  • From DE 41 42 120 A1 is a cooling water pump for an internal combustion engine known.
  • a displaceable in the axial direction Inserted cover ring In one between a water-carrying channel and a water pump housing arranged opening is a displaceable in the axial direction Inserted cover ring.
  • the cover ring is controlled by an actuator depending on Parameters of the internal combustion engine adjustable.
  • By shifting the Deckringes is the width of a gap between the ring and the impeller of Variable water pump, so that the cooling water flow rate is changeable. This makes it possible to shorten the warm-up phase of the internal combustion engine and the Reduce amount of harmful exhaust gas components.
  • the disadvantage is that for Change in the position of the bezel a significant control technology Effort is required.
  • cooling water pumps of internal combustion engines are designed that even at relatively low engine speeds high coolant flows can be provided.
  • the subsidized Volume flow but also the power consumption of the pump much higher than required, which has a negative effect on fuel consumption. apart Of these, cavitation phenomena may occur in the high speed range.
  • the object of the invention is the simplest possible way the flow rate and to reduce the power consumption at high speeds.
  • this is achieved in that the cover ring automatically in dependence the pressure difference between the pressure and suction side of the impeller adjustable is.
  • the gap between impeller and housing is independent adapted to the current impeller speed, thereby consuming actuators can be omitted.
  • an at least formed by a return element restoring force in the direction of the first End position acts on the cover ring.
  • the return element by a resilient biasing means, preferably a return spring, is formed, which acts in the direction of the impeller axis on the cover ring.
  • the cover ring in at least one defined position, preferably at least in the first end position, by a positioning element preferably formed by a latching device is positionable.
  • a positioning element preferably formed by a latching device
  • the positioning element a about spring-loaded radially with respect to the wheel axis, preferably by a Ball formed pressure body, which along a guide surface is slidably disposed and which in the defined position with a reciprocal shaped latching element cooperates.
  • the locking element can, for example to be a bulge in the guide surface.
  • the Guide surface is formed by a suction-side inner surface of the housing and the pressure body is arranged in the jacket region of the cover ring, wherein preferably a pressure spring acting on the pressure body in a radial bore the cover ring is arranged.
  • the guide surface through the cladding region of Deckringes is formed and that the pressure body in the region of a suction chamber side Inner surface of the housing is arranged, preferably one on the Pressure element acting pressure spring disposed in a radial bore of the housing is.
  • the guide surface with respect to the impeller axis by an angle smaller than about 20 °, preferably less than about 10 ° is inclined.
  • the radial pump 1 has a housing 2, in which a shaft 3 for driving an impeller 4 is rotatably supported by a bearing 5.
  • the suction side the radial pump 1 is denoted by reference numeral 6, the pressure side by reference numeral 7th designated.
  • Around the impeller 4 around the housing 2 forms a spiral channel. 8 out.
  • On the suction side 6 of the impeller 4 is in the housing 2, a cover ring 9 in Direction of the impeller axis 10 between a first and a second end position slidably arranged. In the first end position shown in Fig. 1 is a formed between the impeller 4 and housing 2 gap 11 through the cover ring. 9 obscured, so that leakage flows between the pressure side 7 and suction side 6 prevented become.
  • the cover ring 9 is replaced by at least one return element 12 in the first end position moved or held in this.
  • the return element shown in Fig. 2 12 consists of a formed by a spring plate return spring 14, which acts in the axial direction on the cover ring 9.
  • the positioning element shown in Fig. 3 13 is arranged in the jacket region 15 of the cover ring 9 and has a by a compression spring 16 spring-loaded pressure body 17, wherein the compression spring 16 arranged in a radial bore 18 in the jacket region 15 of the cover ring 9 is.
  • the pressure body 17 can be formed for example by a ball his.
  • the pressure body 17 lies on a through a suction-side inner surface 2a of the housing 2 formed guide surface 19 and slides at axial deflection the cover ring along this, wherein the pressure body 17 in the first End position engages in a formed by a recess 20 form element and thus stabilizing the position of the cover ring 9.
  • To the return movement of the To support the cover ring 9 in the direction of the first end position is the guide surface 19 formed with respect to the impeller axis 10 slightly inclined, wherein the angle ⁇ between the guide surface 19 and the impeller axis 10 is smaller than about 10 ° is.
  • the first end position of the cover ring 9 is located at a through the housing 2 stop 21 formed.
  • the cover ring 9 is moved in response to the pressure difference between the pressure p 2 of the pressure side 7 and the pressure p 1 of the suction side 6 from the first end position determining a rest position in the second end position.
  • the cover ring 9 Up to a predefined rotational speed of the impeller 4, which is associated with a certain flow rate, the cover ring 9 is positioned in the first end position shown in Fig. 1 with a very small gap 11 with respect to the impeller 4, so that an optimum efficiency is achieved.
  • This position is defined on the one hand by the stop 21 in the housing, on the other hand by the return element 12 and the positioning element 13.
  • the return element 12 and the positioning element 13 can also be used in combination in order to ensure a demand-oriented control characteristic.
  • the reset and positioning elements 12, 13 are designed so that at a certain pressure difference p 2 - p 1, an axial displacement of the cover ring 9 takes place away from the impeller 4. Depending on the design of the reset and positioning elements 12, 13, this axial adjustment can take place continuously or abruptly above a certain speed.
  • the increasing axial gap 11 between the impeller 4 and cover ring 9 causes a reduction of the flow rate and thereby a reduction of the Power consumption at high speeds. Furthermore, the high speed range prevents cavitation occurring.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Diaphragms For Electromechanical Transducers (AREA)

Abstract

The radial pump (1) has a rotatably mounted shaft driven impeller (4) with a cover ring (9) mounted on the suction side of the impeller and movable between two end positions. The cover ring is automatically adjustable depending upon the pressure difference between the pressure and suction side (7,6) of the impeller. The cover ring in at least one defined position, preferably at least in the first end position, is positioned by a positioning element (13) formed preferably by a locking device.

Description

Die Erfindung betrifft eine Radialpumpe mit einem Gehäuse, in welchem ein durch eine Welle angetriebenes Laufrad drehbar gelagert ist, mit einem auf der Saugseite des Laufrades im Gehäuse axial in Richtung der Laufradachse zwischen zwei Endlagen verschiebbar gelagerten Deckring, wobei durch Verschieben des Deckringes aus einer durch einen Gehäuseanschlag begrenzten ersten Endlage ein zwischen Laufrad und Gehäuse ausgebildeter Spalt freigebbar ist.The invention relates to a radial pump with a housing in which a is rotatably supported by a shaft driven impeller, with a on the Suction side of the impeller in the housing axially in the direction of the impeller axis between two end positions slidably mounted cover ring, wherein by moving the Cover ring from a limited by a housing stop first end position a gap formed between the impeller and the housing can be released.

Aus der DE 41 42 120 A1 ist eine Kühlwasserpumpe für eine Brennkraftmaschine bekannt. In eine zwischen einem wasserführenden Kanal und einem Wasserpumpengehäuse angeordnete Öffnung ist ein in axialer Richtung verschiebbarer Deckring eingesetzt. Der Deckring ist durch ein Stellglied in Abhängigkeit von Parametern der Brennkraftmaschine verstellbar. Durch die Verschiebung des Deckringes ist die Breite eines Spaltes zwischen dem Ring und dem Laufrad der Wasserpumpe variabel, so dass der Kühlwasserdurchsatz veränderbar ist. Dies ermöglicht es, die Warmlaufphase der Brennkraftmaschine zu verkürzen und die Menge der schädlichen Abgasbestandteile zu verringern. Nachteilig ist, dass zur Veränderung der Lage des Deckringes ein erheblicher steuerungstechnischer Aufwand erforderlich ist.From DE 41 42 120 A1 is a cooling water pump for an internal combustion engine known. In one between a water-carrying channel and a water pump housing arranged opening is a displaceable in the axial direction Inserted cover ring. The cover ring is controlled by an actuator depending on Parameters of the internal combustion engine adjustable. By shifting the Deckringes is the width of a gap between the ring and the impeller of Variable water pump, so that the cooling water flow rate is changeable. This makes it possible to shorten the warm-up phase of the internal combustion engine and the Reduce amount of harmful exhaust gas components. The disadvantage is that for Change in the position of the bezel a significant control technology Effort is required.

Insbesondere Kühlwasserpumpen von Brennkraftmaschinen sind so konzipiert, dass bereits bei relativ niedrigen Motordrehzahlen hohe Kühlmitteldurchflüsse bereitgestellt werden können. Bei hohen Motordrehzahlen ist der geförderte Volumenstrom, aber auch die Leistungsaufnahme der Pumpe viel höher als erforderlich, was sich nachteilig auf den Kraftstoffverbrauch auswirkt. Abgesehen davon, kann es im hohen Drehzahlbereich zu Kavitationserscheinungen kommen.In particular, cooling water pumps of internal combustion engines are designed that even at relatively low engine speeds high coolant flows can be provided. At high engine speeds, the subsidized Volume flow, but also the power consumption of the pump much higher than required, which has a negative effect on fuel consumption. apart Of these, cavitation phenomena may occur in the high speed range.

Aufgabe der Erfindung ist es, auf möglichst einfache Weise die Durchflussmenge und die Leistungsaufnahme bei hohen Drehzahlen zu vermindern.The object of the invention is the simplest possible way the flow rate and to reduce the power consumption at high speeds.

Erfindungsgemäß wird dies dadurch erreicht, dass der Deckring selbsttätig in Abhängigkeit der Druckdifferenz zwischen Druck- und Saugseite des Laufrades verstellbar ist. Durch den durch die Druckdifferenz zwischen Druck- und Saugseite verschiebbaren Deckring wird der Spalt zwischen Laufrad und Gehäuse selbständig der aktuellen Laufraddrehzahl angepasst, wodurch aufwendige Stellglieder entfallen können.According to the invention this is achieved in that the cover ring automatically in dependence the pressure difference between the pressure and suction side of the impeller adjustable is. By the pressure difference between the pressure and suction sides sliding cover ring, the gap between impeller and housing is independent adapted to the current impeller speed, thereby consuming actuators can be omitted.

Gemäß der Erfindung ist weiters vorgesehen, dass auf den Deckring eine zumindest durch ein Rückstellelement gebildete Rückstellkraft in Richtung der ersten Endlage einwirkt. Vorzugsweise ist dabei vorgesehen, dass das Rückstellelement durch eine elastische Vorspanneinrichtung, vorzugsweise eine Rückstellfeder, gebildet ist, welche in Richtung der Laufradachse auf den Deckring einwirkt.According to the invention, it is further provided that on the cover ring an at least formed by a return element restoring force in the direction of the first End position acts. Preferably, it is provided that the return element by a resilient biasing means, preferably a return spring, is formed, which acts in the direction of the impeller axis on the cover ring.

In weiterer Ausführung der Erfindung kann vorgesehen sein, dass der Deckring in zumindest einer definierten Lage, vorzugsweise zumindest in der ersten Endlage, durch ein vorzugsweise durch eine Rasteinrichtung gebildetes Positionierelement positionierbar ist. Dadurch können Flattererscheinungen des Deckringes in bestimmten Drehzahlbereichen, welche ein zyklisches Öffnen und Schließen des Spaltes zwischen Gehäuse und Laufrad bewirken würden, verhindert werden. Vorteilhafter Weise ist dabei vorgesehen sein, dass das Positionierelement einen etwa radial bezüglich der Laufradachse federbelasteten, vorzugsweise durch eine Kugel gebildeten Druckkörper aufweist, welcher entlang einer Führungsfläche gleitbar angeordnet ist und welches in der definierten Lage mit einem reziprok geformten Rastelement zusammenwirkt. Das Rastelement kann beispielsweise eine Ausbuchtung in der Führungsfläche sein.In a further embodiment of the invention can be provided that the cover ring in at least one defined position, preferably at least in the first end position, by a positioning element preferably formed by a latching device is positionable. This allows fluttering of the bezel in certain Speed ranges, which is a cyclic opening and closing of the Gap between housing and impeller would cause prevented. Advantageously, it can be provided that the positioning element a about spring-loaded radially with respect to the wheel axis, preferably by a Ball formed pressure body, which along a guide surface is slidably disposed and which in the defined position with a reciprocal shaped latching element cooperates. The locking element can, for example to be a bulge in the guide surface.

In einer besonders vorteilhaften Ausführungsvariante ist vorgesehen, dass die Führungsfläche durch eine saugseitige Innenfläche des Gehäuses gebildet ist und der Druckkörper im Mantelbereich des Deckringes angeordnet ist, wobei vorzugsweise eine auf den Druckkörper wirkende Druckfeder in einer radialen Bohrung des Deckringes angeordnet ist. Gemäß einer dazu reziproken Ausführungsvariante ist vorgesehen, dass die Führungsfläche durch den Mantelbereich des Deckringes gebildet ist und dass der Druckkörper im Bereich einer saugraumseitigen Innenfläche des Gehäuses angeordnet ist, wobei vorzugsweise eine auf den Druckkörper einwirkende Druckfeder in einer radialen Bohrung des Gehäuses angeordnet ist.In a particularly advantageous embodiment, it is provided that the Guide surface is formed by a suction-side inner surface of the housing and the pressure body is arranged in the jacket region of the cover ring, wherein preferably a pressure spring acting on the pressure body in a radial bore the cover ring is arranged. According to a reciprocal embodiment variant is provided that the guide surface through the cladding region of Deckringes is formed and that the pressure body in the region of a suction chamber side Inner surface of the housing is arranged, preferably one on the Pressure element acting pressure spring disposed in a radial bore of the housing is.

Um die Rückstellbewegung des Deckringes zu unterstützen, ist es vorteilhaft, wenn die Führungsfläche bezüglich der Laufradachse um einen Winkel kleiner als etwa 20°, vorzugsweise kleiner als etwa 10° geneigt ist.To assist the return movement of the bezel, it is advantageous when the guide surface with respect to the impeller axis by an angle smaller than about 20 °, preferably less than about 10 ° is inclined.

Die Erfindung wird im Folgenden anhand der Figuren näher erläutert. Es zeigen

Fig. 1
eine erfindungsgemäße Radialpumpe in einem Längsschnitt,
Fig. 2
das Detail II aus Fig. 1 und
Fig. 3
das Detail III aus Fig. 1.
The invention will be explained in more detail below with reference to FIGS. Show it
Fig. 1
a radial pump according to the invention in a longitudinal section,
Fig. 2
the detail II of Fig. 1 and
Fig. 3
the detail III of FIG. 1.

Die Radialpumpe 1 weist ein Gehäuse 2 auf, in welchem eine Welle 3 zum Antrieb eines Laufrades 4 mittels eines Lagers 5 drehbar gelagert ist. Die Saugseite der Radialpumpe 1 ist mit Bezugszeichen 6, die Druckseite mit Bezugszeichen 7 bezeichnet. Um das Laufrad 4 herum bildet das Gehäuse 2 einen Spiralkanal 8 aus. Auf der Saugseite 6 des Laufrades 4 ist im Gehäuse 2 ein Deckring 9 in Richtung der Laufradachse 10 zwischen einer ersten und einer zweiten Endlage verschiebbar angeordnet. In der in Fig. 1 dargestellten ersten Endlage wird ein zwischen Laufrad 4 und Gehäuse 2 ausgebildeter Spalt 11 durch den Deckring 9 verdeckt, so dass Leckageströme zwischen Druckseite 7 und Saugseite 6 unterbunden werden.The radial pump 1 has a housing 2, in which a shaft 3 for driving an impeller 4 is rotatably supported by a bearing 5. The suction side the radial pump 1 is denoted by reference numeral 6, the pressure side by reference numeral 7th designated. Around the impeller 4 around the housing 2 forms a spiral channel. 8 out. On the suction side 6 of the impeller 4 is in the housing 2, a cover ring 9 in Direction of the impeller axis 10 between a first and a second end position slidably arranged. In the first end position shown in Fig. 1 is a formed between the impeller 4 and housing 2 gap 11 through the cover ring. 9 obscured, so that leakage flows between the pressure side 7 and suction side 6 prevented become.

Der Deckring 9 wird durch zumindest ein Rückstellelement 12 in die erste Endlage bewegt bzw. in dieser festgehalten. Das in Fig. 2 dargestellte Rückstellelement 12 besteht aus einer durch ein Federblech gebildeten Rückstellfeder 14, welche in axialer Richtung auf den Deckring 9 einwirkt.The cover ring 9 is replaced by at least one return element 12 in the first end position moved or held in this. The return element shown in Fig. 2 12 consists of a formed by a spring plate return spring 14, which acts in the axial direction on the cover ring 9.

Durch ein Positionierelement 13 wird der Deckring 9 in einer vordefinierten Lage, etwa der ersten Endlage, gehalten. Dadurch wird ein Flattern des Deckringes 9 bei kritischen Drehzahlen verhindert. Das in Fig. 3 dargestellte Positionierelement 13 ist im Mantelbereich 15 des Deckringes 9 angeordnet und weist einen durch eine Druckfeder 16 federbelasteten Druckkörper 17 auf, wobei die Druckfeder 16 in einer radialen Bohrung 18 im Mantelbereich 15 des Deckringes 9 angeordnet ist. Der Druckkörper 17 kann beispielsweise durch eine Kugel gebildet sein. Der Druckkörper 17 liegt auf einer durch eine saugseitige Innenfläche 2a des Gehäuses 2 gebildeten Führungsfläche 19 auf und gleitet bei axialer Auslenkung des Deckringes an dieser entlang, wobei der Druckkörper 17 in der ersten Endlage in ein durch eine Einbuchtung 20 gebildetes Formelement einrastet und somit die Position des Deckringes 9 stabilisiert. Um die Rückstellbewegung des Deckringes 9 in Richtung der ersten Endlage zu unterstützen, ist die Führungsfläche 19 bezüglich der Laufradachse 10 leicht geneigt ausgebildet, wobei der Winkel α zwischen der Führungsfläche 19 und der Laufradachse 10 kleiner als etwa 10° ist. In der ersten Endlage liegt der Deckring 9 an einem durch das Gehäuse 2 gebildeten Anschlag 21 an.By a positioning member 13 of the cover ring 9 in a predefined position, about the first end position, held. As a result, a flutter of the cover ring. 9 prevented at critical speeds. The positioning element shown in Fig. 3 13 is arranged in the jacket region 15 of the cover ring 9 and has a by a compression spring 16 spring-loaded pressure body 17, wherein the compression spring 16 arranged in a radial bore 18 in the jacket region 15 of the cover ring 9 is. The pressure body 17 can be formed for example by a ball his. The pressure body 17 lies on a through a suction-side inner surface 2a of the housing 2 formed guide surface 19 and slides at axial deflection the cover ring along this, wherein the pressure body 17 in the first End position engages in a formed by a recess 20 form element and thus stabilizing the position of the cover ring 9. To the return movement of the To support the cover ring 9 in the direction of the first end position is the guide surface 19 formed with respect to the impeller axis 10 slightly inclined, wherein the angle α between the guide surface 19 and the impeller axis 10 is smaller than about 10 ° is. In the first end position of the cover ring 9 is located at a through the housing 2 stop 21 formed.

Der Deckring 9 wird in Abhängigkeit der Druckdifferenz zwischen dem Druck p2 der Druckseite 7 und dem Druck p1 der Saugseite 6 aus der eine Ruhelage bestimmenden ersten Endlage in die zweite Endlage bewegt. Bis zu einer vordefinierten Drehzahl des Laufrades 4, welcher eine bestimmte Durchflussmenge zugeordnet ist, ist der Deckring 9 in der in Fig. 1 dargestellten ersten Endlage mit sehr geringem Spalt 11 bezüglich dem Laufrad 4 positioniert, so dass ein optimaler Wirkungsgrad erreicht wird. Diese Position wird einerseits durch den Anschlag 21 im Gehäuse, andererseits durch das Rückstellelement 12 und das Positionierelement 13 definiert. Je nach Auslegung können Rückstellelement 12 und Positionierelement 13 auch kombiniert angewendet werden, um eine bedarfsgerechte Regelcharakteristik zu gewährleisten.The cover ring 9 is moved in response to the pressure difference between the pressure p 2 of the pressure side 7 and the pressure p 1 of the suction side 6 from the first end position determining a rest position in the second end position. Up to a predefined rotational speed of the impeller 4, which is associated with a certain flow rate, the cover ring 9 is positioned in the first end position shown in Fig. 1 with a very small gap 11 with respect to the impeller 4, so that an optimum efficiency is achieved. This position is defined on the one hand by the stop 21 in the housing, on the other hand by the return element 12 and the positioning element 13. Depending on the design, the return element 12 and the positioning element 13 can also be used in combination in order to ensure a demand-oriented control characteristic.

Die Rückstell- und Positionierelemente 12, 13 sind so ausgelegt, dass bei einer bestimmten Druckdifferenz p2 - p1 eine axiale Verschiebung des Deckringes 9 vom Laufrad 4 weg stattfindet. Je nach Auslegung der Rückstell- und Positionierelemente 12, 13 kann diese axiale Verstellung kontinuierlich oder ab einer bestimmten Drehzahl abrupt erfolgen.The reset and positioning elements 12, 13 are designed so that at a certain pressure difference p 2 - p 1, an axial displacement of the cover ring 9 takes place away from the impeller 4. Depending on the design of the reset and positioning elements 12, 13, this axial adjustment can take place continuously or abruptly above a certain speed.

Der sich vergrößernde axiale Spalt 11 zwischen Laufrad 4 und Deckring 9 bewirkt eine Reduzierung der Durchflussmenge und dadurch auch eine Reduzierung der Leistungsaufnahme bei hohen Drehzahlen. Weiters wird die im hohen Drehzahlbereich auftretende Kavitation verhindert.The increasing axial gap 11 between the impeller 4 and cover ring 9 causes a reduction of the flow rate and thereby a reduction of the Power consumption at high speeds. Furthermore, the high speed range prevents cavitation occurring.

Claims (8)

Radialpumpe (1) mit einem Gehäuse (2), in welchem ein durch eine Welle (3) angetriebenes Laufrad (4) drehbar gelagert ist, mit einem auf der Saugseite (6) des Laufrades (4) im Gehäuse (2) axial in Richtung der Laufradachse (10) zwischen zwei Endlagen verschiebbar gelagerten Deckring (9), wobei durch Verschieben des Deckringes (9) aus einer durch einen Gehäuseanschlag (21) begrenzten ersten Endlage ein zwischen Laufrad (4) und Gehäuse (2) ausgebildeter Spalt (11) freigebbar ist, dadurch gekennzeichnet, dass der Deckring (9) selbsttätig in Abhängigkeit der Druckdifferenz zwischen Druck- und Saugseite (7, 6) des Laufrades (4) verstellbar ist.Radial pump (1) with a housing (2) in which an impeller (4) driven by a shaft (3) is rotatably mounted, with one on the suction side (6) of the impeller (4) in the housing (2) axially in the direction the impeller axis (10) between two end positions slidably mounted cover ring (9), wherein by moving the cover ring (9) from a by a housing stop (21) limited first end position between an impeller (4) and housing (2) formed gap (11) is releasable, characterized in that the cover ring (9) automatically in dependence of the pressure difference between the pressure and suction side (7, 6) of the impeller (4) is adjustable. Radialpumpe (1) nach Anspruch 1, dadurch gekennzeichnet, dass auf den Deckring (9) eine zumindest durch ein Rückstellelement (12) gebildete Rückstellkraft in Richtung der ersten Endlage einwirkt.Radial pump (1) according to claim 1, characterized in that on the cover ring (9) at least by a return element (12) formed restoring force acts in the direction of the first end position. Radialpumpe (1) nach Anspruch 2, dadurch gekennzeichnet, dass das Rückstellelement (12) durch eine elastische Vorspanneinrichtung, vorzugsweise eine Rückstellfeder (14), gebildet ist, welche in Richtung der Laufradachse (10) auf den Deckring (9) einwirkt.Radial pump (1) according to claim 2, characterized in that the return element (12) by a resilient biasing means, preferably a return spring (14) is formed, which acts in the direction of the impeller axis (10) on the cover ring (9). Radialpumpe (1) nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, dass der Deckring (9) in zumindest einer definierten Lage, vorzugsweise zumindest in der ersten Endlage, durch ein vorzugsweise durch eine Rasteinrichtung gebildetes Positionierelement (13) positionierbar ist.Radial pump (1) according to one of claims 1 to 3, characterized in that the cover ring (9) can be positioned in at least one defined position, preferably at least in the first end position, by a positioning element (13) preferably formed by a latching device. Radialpumpe (1) nach Anspruch 4, dadurch gekennzeichnet, dass das Positionierelement (13) einen etwa radial bezüglich der Laufradachse (10) federbelasteten, vorzugsweise durch eine Kugel gebildeten Druckkörper (17) aufweist, welcher in der definierten Lage mit einem reziprok geformten Rastelement zusammenwirkt und entlang einer Führungsfläche (19) gleitbar angeordnet ist, wobei das Rastelement vorzugsweise durch eine Einbuchtung (20) in der Führungsfläche (19) gebildet ist.Radial pump (1) according to claim 4, characterized in that the positioning element (13) has an approximately radially with respect to the impeller axis (10) spring-loaded, preferably formed by a ball pressure body (17) which cooperates in the defined position with a reciprocally shaped locking element and is slidably disposed along a guide surface (19), wherein the latching element is preferably formed by a recess (20) in the guide surface (19). Radialpumpe (1) nach Anspruch 5, dadurch gekennzeichnet, dass die Führungsfläche (19) durch eine saugseitige Innenfläche (2a) des Gehäuses (2) gebildet ist und der Druckkörper (17) im Mantelbereich (15) des Deckringes (9) angeordnet ist, wobei vorzugsweise eine auf den Druckkörper (17) wirkende Druckfeder (16) in einer radialen Bohrung (18) des Deckringes (9) angeordnet ist. Radial pump (1) according to claim 5, characterized in that the guide surface (19) by a suction-side inner surface (2a) of the housing (2) is formed and the pressure body (17) in the jacket region (15) of the cover ring (9) is arranged wherein preferably on the pressure body (17) acting compression spring (16) in a radial bore (18) of the cover ring (9) is arranged. Radialpumpe (1) nach Anspruch 5, dadurch gekennzeichnet, dass die Führungsfläche (19) durch den Mantelbereich (15) des Deckringes (9) gebildet ist und dass der Druckkörper (17) im Bereich einer saugraumseitigen Innenfläche (2a) des Gehäuses (2) angeordnet ist, wobei vorzugsweise eine auf den Druckkörper (17) einwirkende Druckfeder (16) in einer radialen Bohrung (18) des Gehäuses (2) angeordnet ist.Radial pump (1) according to claim 5, characterized in that the guide surface (19) through the jacket portion (15) of the cover ring (9) is formed and that the pressure body (17) in the region of a suction-side inner surface (2a) of the housing (2) is arranged, wherein preferably on the pressure body (17) acting compression spring (16) in a radial bore (18) of the housing (2) is arranged. Radialpumpe (1) nach einem der Ansprüche 5 bis 7, dadurch gekennzeichnet, dass die Führungsfläche (19) bezüglich der Laufradachse (10) um einen Winkel (α) kleiner als etwa 20°, vorzugsweise kleiner als etwa 10° geneigt ist.Radial pump (1) according to one of claims 5 to 7, characterized in that the guide surface (19) with respect to the impeller axis (10) by an angle (α) is less than about 20 °, preferably less than about 10 ° inclined.
EP03450273A 2003-12-04 2003-12-04 Radial pump Expired - Lifetime EP1538338B1 (en)

Priority Applications (6)

Application Number Priority Date Filing Date Title
DE50303864T DE50303864D1 (en) 2003-12-04 2003-12-04 radial pump
EP03450273A EP1538338B1 (en) 2003-12-04 2003-12-04 Radial pump
AT03450273T ATE330127T1 (en) 2003-12-04 2003-12-04 RADIAL PUMP
AT04450193T ATE346240T1 (en) 2003-12-04 2004-10-14 RADIAL PUMP
DE502004002076T DE502004002076D1 (en) 2003-12-04 2004-10-14 radial pump
EP20040450193 EP1538339B1 (en) 2003-12-04 2004-10-14 Radial pump

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP03450273A EP1538338B1 (en) 2003-12-04 2003-12-04 Radial pump

Publications (2)

Publication Number Publication Date
EP1538338A1 true EP1538338A1 (en) 2005-06-08
EP1538338B1 EP1538338B1 (en) 2006-06-14

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ID=34443181

Family Applications (1)

Application Number Title Priority Date Filing Date
EP03450273A Expired - Lifetime EP1538338B1 (en) 2003-12-04 2003-12-04 Radial pump

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Country Link
EP (1) EP1538338B1 (en)
AT (2) ATE330127T1 (en)
DE (2) DE50303864D1 (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9869326B2 (en) 2012-12-05 2018-01-16 Wilo Se Centrifugal pump in particular for waste water or polluted water

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2786420A (en) * 1952-03-27 1957-03-26 Stanley G Harwood Pressure controlled pump
US3168870A (en) * 1962-12-12 1965-02-09 Ingersoll Rand Co Centrifugal pump with adjustable capacity
DE1528821A1 (en) * 1962-10-15 1969-10-16 Sulzer Ag Process for influencing the start-up process of a single-stage, single-flow pump or reversible pump turbine as well as pump or pump turbine for carrying out the process
FR2681906A1 (en) * 1991-09-27 1993-04-02 Renault Vehicules Ind Centrifugal pump for a combustion engine coolant circuit
DE4142120A1 (en) * 1991-12-20 1993-06-24 Porsche Ag Coolant pump with movable ring for IC engine - has cross=section of flow into pump rotor adjustable in accordance with engine temp. and load

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2786420A (en) * 1952-03-27 1957-03-26 Stanley G Harwood Pressure controlled pump
DE1528821A1 (en) * 1962-10-15 1969-10-16 Sulzer Ag Process for influencing the start-up process of a single-stage, single-flow pump or reversible pump turbine as well as pump or pump turbine for carrying out the process
US3168870A (en) * 1962-12-12 1965-02-09 Ingersoll Rand Co Centrifugal pump with adjustable capacity
FR2681906A1 (en) * 1991-09-27 1993-04-02 Renault Vehicules Ind Centrifugal pump for a combustion engine coolant circuit
DE4142120A1 (en) * 1991-12-20 1993-06-24 Porsche Ag Coolant pump with movable ring for IC engine - has cross=section of flow into pump rotor adjustable in accordance with engine temp. and load

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9869326B2 (en) 2012-12-05 2018-01-16 Wilo Se Centrifugal pump in particular for waste water or polluted water

Also Published As

Publication number Publication date
DE502004002076D1 (en) 2007-01-04
EP1538338B1 (en) 2006-06-14
ATE330127T1 (en) 2006-07-15
ATE346240T1 (en) 2006-12-15
DE50303864D1 (en) 2006-07-27

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