EP1538339A1 - Radial pump - Google Patents

Radial pump Download PDF

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Publication number
EP1538339A1
EP1538339A1 EP04450193A EP04450193A EP1538339A1 EP 1538339 A1 EP1538339 A1 EP 1538339A1 EP 04450193 A EP04450193 A EP 04450193A EP 04450193 A EP04450193 A EP 04450193A EP 1538339 A1 EP1538339 A1 EP 1538339A1
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EP
European Patent Office
Prior art keywords
cover ring
radial pump
housing
impeller
ring
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
EP04450193A
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German (de)
French (fr)
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EP1538339B1 (en
Inventor
Alfred Götschhofer
Fritz Dipl.-Ing. Atschreiter
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TCG Unitech Systemtechnik GmbH
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TCG Unitech Systemtechnik GmbH
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Filing date
Publication date
Priority claimed from EP03450273A external-priority patent/EP1538338B1/en
Application filed by TCG Unitech Systemtechnik GmbH filed Critical TCG Unitech Systemtechnik GmbH
Priority to EP20040450193 priority Critical patent/EP1538339B1/en
Publication of EP1538339A1 publication Critical patent/EP1538339A1/en
Application granted granted Critical
Publication of EP1538339B1 publication Critical patent/EP1538339B1/en
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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 is releasable, wherein the Cover ring automatically depending on the pressure difference between pressure and Suction side of the impeller is adjustable.
  • cooling water pumps of internal combustion engines are designed that even at relatively low engine speeds high coolant flows can be provided.
  • the delivered volume flow but also the power consumption of the pump much higher than required, which has a negative effect on fuel consumption. Apart from this, It can come in the high speed range to cavitation phenomena.
  • 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 by a pressure box exhibiting Adjustable actuator in dependence on parameters of the internal combustion engine. Due to the displacement of the cover ring is the width of a gap between the Ring and the impeller of the water pump variable, so that the cooling water flow rate is changeable. This allows the warm-up phase of the internal combustion engine to shorten and reduce the amount of harmful exhaust gas constituents.
  • US 2,786,420 A describes a radial pump, wherein by means of a Pressure box a cover ring depending on the pressure difference between pressure and Suction side can be adjusted.
  • the object of the invention is the simplest possible way the flow rate and to reduce the power consumption at high speeds while a to ensure stable operation.
  • the cover ring in at least one defined position, preferably at least in the first end position, by a preferably positioned by a locking device positioning positioned is.
  • This allows fluttering of the bezel in certain Speed ranges, which is a cyclic opening and closing of the gap between Case and impeller cause would be prevented.
  • the positioning at least one has spring-loaded pressure body approximately radially with respect to the impeller axis, which cooperates in the defined position with a reciprocally shaped locking element and slidably disposed along a guide surface, wherein the latching element is preferably formed by a recess in the guide surface is.
  • the Guide surface is formed by a suction-side inner surface of the housing and the pressure body is arranged in the jacket area of the cover ring.
  • the guide surface is formed by the shell region of the cover ring and that the pressure body is arranged in the region of a suction chamber-side inner surface of the housing.
  • the guide surface with respect to the impeller axis by an angle smaller than about 20 °, preferably less than about 10 ° is inclined.
  • a pressure spring acting on the pressure body can be in a radial bore be arranged of the cover ring or the housing.
  • the pressure body has a convex surface.
  • the short-circuit channel can be formed by at least one molding in the housing and / or be formed in the cover ring.
  • the short-circuit channel is thereby by the Decking is controlled and designed so that the flow area with the deflection of the bezel increases. This ensures that in the upper Speed range are controlled relatively large flow rates, causing the Power consumption of the radial pump significantly reduced in this operating range can be.
  • the gap between the impeller and housing is independent of the adjusted current impeller speed, thereby eliminating complex actuators can.
  • 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 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 may, for example, by a ball or Hemisphere 17a be formed.
  • the pressure body 17 is located on a suction side Inner surface 2a of the housing 2 formed guide surface 19 and slides at axial deflection of the cover ring along this, wherein the Pressure element 17 in the first end position in a formed by a recess 20 Form element engages and thus stabilizes the position of the cover ring 9.
  • the guide surface 19 with respect to the impeller axis 10 is slightly inclined formed, wherein the angle ⁇ between the guide surface 19 and the Impeller shaft 10 is less than about 10 °.
  • the cover ring 9 In the first end position is the cover ring 9 on a stop 21 formed by the housing 2.
  • 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.
  • FIG. 4 and FIG. 5 show an embodiment in which the pressure body 17 is formed by a spring ring 17b (Fig. 6), which in a circumferential Ring groove 22 of the cover ring 9 is arranged.
  • the housing 2 has at least one short-circuit channel 23, which in the deflection of the cover ring 9 shown in Fig. 5, the flow connection according to the arrow S between the pressure side 7 and suction side 6 of the radial pump 1 allows.
  • the shorting channel 23 is defined by an edge 24 of the Deckringes 9 is controlled and is designed so that the flow cross-section increases with the size of the deflection of the cover ring 9. This will be added high speeds relatively large amounts of the pumped medium.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Abstract

The pump has a housing (2) with driven rotor (4) and cover ring (9). Movement of the ring by a pressure differential opens a gap (11) between rotor and housing. The ring is moved into a defined position, pref. a first end position, by a positioner element (13) formed pref. by a locking device. The ring is also loaded in direction of that position, by a return force applied by a return element (12). This is pref. a spring, acting on the ring in direction of the rotor axis.

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, wobei der Deckring selbsttätig in Abhängigkeit der Druckdifferenz zwischen Druck- und Saugseite des Laufrades verstellbar 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 is releasable, wherein the Cover ring automatically depending on the pressure difference between pressure and Suction side of the impeller is adjustable.

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 delivered volume flow, but also the power consumption of the pump much higher than required, which has a negative effect on fuel consumption. Apart from this, It can come in the high speed range to cavitation phenomena.

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 eine Druckdose aufweisendes 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.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 by a pressure box exhibiting Adjustable actuator in dependence on parameters of the internal combustion engine. Due to the displacement of the cover ring is the width of a gap between the Ring and the impeller of the water pump variable, so that the cooling water flow rate is changeable. This allows the warm-up phase of the internal combustion engine to shorten and reduce the amount of harmful exhaust gas constituents.

Auch die US 2,786,420 A beschreibt eine Radialpumpe, bei der mittels einer Druckdose ein Deckring in Abhängigkeit der Druckdifferenz zwischen Druck- und Saugseite verstellt werden kann.Also, US 2,786,420 A describes a radial pump, wherein by means of a Pressure box a cover ring depending on the pressure difference between pressure and Suction side can be adjusted.

Durch Druckfluktuationen kann es aber in bestimmten Drehzahlbereichen zu zylindrischen Verstellbewegungen des Deckringes kommen, was sich nachteilig auf den stabilen Betrieb auswirkt. Due to pressure fluctuations but it can be too cylindrical in certain speed ranges Adjusting movements of the cover ring come, which is disadvantageous the stable operation.

Aufgabe der Erfindung ist es, auf möglichst einfache Weise die Durchflussmenge und die Leistungsaufnahme bei hohen Drehzahlen zu vermindern und dabei einen stabilen Betrieb zu gewährleisten.The object of the invention is the simplest possible way the flow rate and to reduce the power consumption at high speeds while a to ensure stable operation.

Erfindungsgemäß wird dies dadurch erreicht, 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 zumindest einen etwa radial bezüglich der Laufradachse federbelasteten Druckkörper aufweist, welcher in der definierten Lage mit einem reziprok geformten Rastelement zusammenwirkt und entlang einer Führungsfläche gleitbar angeordnet ist, wobei das Rastelement vorzugsweise durch eine Einbuchtung in der Führungsfläche gebildet ist.According to the invention this is achieved in that the cover ring in at least one defined position, preferably at least in the first end position, by a preferably positioned by a locking device positioning positioned is. This allows fluttering of the bezel in certain Speed ranges, which is a cyclic opening and closing of the gap between Case and impeller cause would be prevented. Favorable Way is to be provided that the positioning at least one has spring-loaded pressure body approximately radially with respect to the impeller axis, which cooperates in the defined position with a reciprocally shaped locking element and slidably disposed along a guide surface, wherein the latching element is preferably formed by a recess in the guide surface is.

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. 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.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 area of the cover ring. According to one this reciprocal embodiment variant is provided that the guide surface is formed by the shell region of the cover ring and that the pressure body is arranged in the region of a suction chamber-side inner surface of the housing.

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.

Eine auf den Druckkörper einwirkende Druckfeder kann in einer radialen Bohrung des Deckringes oder des Gehäuses angeordnet sein.A pressure spring acting on the pressure body can be in a radial bore be arranged of the cover ring or the housing.

Gemäß einer einfachen Ausführungsvariante der Erfindung ist vorgesehen, dass der Druckkörper eine konvexe Oberfläche aufweist. Alternativ dazu ist es auch möglich, den Druckkörper als Federring auszubilden, wodurch Teile eingespart werden können.According to a simple embodiment of the invention, it is provided that the pressure body has a convex surface. Alternatively, it is possible to form the pressure body as a spring ring, thereby saving parts can be.

In einer besonders bevorzugten Ausführungsvariante der Erfindung ist vorgesehen, dass im Bereich des Deckringes zumindest ein Kurzschlusskanal angeordnet ist. Der Kurzschlusskanal kann durch zumindest eine Ausformung im Gehäuse und/oder im Deckring gebildet sein. Der Kurzschlusskanal wird dabei durch den Deckring aufgesteuert und ist so gestaltet, dass der Durchflussquerschnitt mit der Auslenkung des Deckringes zunimmt. Dadurch wird erreicht, dass im oberen Drehzahlbereich relativ große Fördermengen abgesteuert werden, wodurch die Leistungsaufnahme der Radialpumpe in diesem Betriebsbereich wesentlich vermindert werden kann.In a particularly preferred embodiment of the invention, it is provided that arranged in the region of the cover ring at least one short-circuit channel is. The short-circuit channel can be formed by at least one molding in the housing and / or be formed in the cover ring. The short-circuit channel is thereby by the Decking is controlled and designed so that the flow area with the deflection of the bezel increases. This ensures that in the upper Speed range are controlled relatively large flow rates, causing the Power consumption of the radial pump significantly reduced in this operating range can be.

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.By the displaceable by the pressure difference between the pressure and suction side Cover ring, the gap between the impeller and housing is independent of the adjusted current impeller speed, thereby eliminating complex actuators can.

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.

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

Fig. 1
eine erfindungsgemäße Radialpumpe in einem Längsschnitt in einer ersten Ausführungsvariante,
Fig. 2
das Detail II aus Fig. 1,
Fig. 3
das Detail III aus Fig. 1,
Fig. 4
eine erfindungsgemäße Radialpumpe gemäß dem Detail aus Fig. 3 in einer zweiten Ausführungsvariante in einer Ruhstellung des Deckringes,
Fig. 5
ein Detail gemäß Fig. 4 in einer Auslenkstellung des Deckringes, und
Fig. 6
ein Positionselement in einer Ausführungsvariante.
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 in a first embodiment,
Fig. 2
the detail II of Fig. 1,
Fig. 3
the detail III of Fig. 1,
Fig. 4
a radial pump according to the invention according to the detail of FIG. 3 in a second embodiment in a rest position of the cover ring,
Fig. 5
a detail of FIG. 4 in a deflection position of the cover ring, and
Fig. 6
a position element in a variant embodiment.

In den Figuren sind funktionsgleiche Teile mit gleichen Bezugszeichen versehen.In the figures, functionally identical parts are provided with the same reference numerals.

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 oder Halbkugel 17a 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 may, for example, by a ball or Hemisphere 17a be formed. The pressure body 17 is located on a suction side Inner surface 2a of the housing 2 formed guide surface 19 and slides at axial deflection of the cover ring along this, wherein the Pressure element 17 in the first end position in a formed by a recess 20 Form element engages and thus stabilizes the position of the cover ring 9. To the return movement of the cover ring 9 in the direction of the first end position support, the guide surface 19 with respect to the impeller axis 10 is slightly inclined formed, wherein the angle α between the guide surface 19 and the Impeller shaft 10 is less than about 10 °. In the first end position is the cover ring 9 on a stop 21 formed by the housing 2.

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.

Fig. 4 und Fig. 5 zeigen ein Ausführungsbeispiel bei dem der Druckkörper 17 durch einen Federring 17b (Fig. 6) gebildet ist, welcher in einer umlaufenden Ringnut 22 des Deckringes 9 angeordnet ist. Im Bereich des Mantels 15 des Deckringes 9 weist das Gehäuse 2 zumindest einen Kurzschlusskanal 23 auf, welcher bei der in Fig. 5 gezeigten Auslenkung des Deckringes 9 die Strömungsverbindung gemäß dem Pfeil S zwischen Druckseite 7 und Saugseite 6 der Radialpumpe 1 ermöglicht. Der Kurzschlusskanal 23 wird von einer Kante 24 des Deckringes 9 aufgesteuert und ist so gestaltet, dass der Durchflussquerschnitt mit der Größe der Auslenkung des Deckringes 9 zunimmt. Dadurch werden bei hohen Drehzahlen relativ große Mengen des Fördermediums abgesteuert.4 and FIG. 5 show an embodiment in which the pressure body 17 is formed by a spring ring 17b (Fig. 6), which in a circumferential Ring groove 22 of the cover ring 9 is arranged. In the area of the coat 15 of the Cover ring 9, the housing 2 has at least one short-circuit channel 23, which in the deflection of the cover ring 9 shown in Fig. 5, the flow connection according to the arrow S between the pressure side 7 and suction side 6 of the radial pump 1 allows. The shorting channel 23 is defined by an edge 24 of the Deckringes 9 is controlled and is designed so that the flow cross-section increases with the size of the deflection of the cover ring 9. This will be added high speeds relatively large amounts of the pumped medium.

Claims (13)

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, wobei der Deckring (9) selbsttätig in Abhängigkeit der Druckdifferenz zwischen Druck- und Saugseite (7, 6) des Laufrades (4) verstellbar ist, dadurch gekennzeichnet, dass der Deckring (9) in zumindest einer definierten Lage, vorzugsweise zumindest in der ersten Endlage, durch ein vorzugsweise durch zumindest eine Rasteinrichtung gebildetes Positionierelement (13) positionierbar 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, wherein 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, characterized in that the cover ring (9) in at least one defined position, preferably at least in the first end position, can be positioned by a preferably formed by at least one latching positioning (13). 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 das Positionierelement (13) zumindest einen etwa radial bezüglich der Laufradachse (10) federbelasteten 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 one of claims 1 to 3, characterized in that the positioning element (13) at least one approximately radially with respect to the impeller shaft (10) spring-loaded 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 locking element is preferably formed by a recess (20) in the guide surface (19). Radialpumpe (1) nach Anspruch 4, dadurch gekennzeichnet, dass zumindest eine auf den Druckkörper (17) einwirkende Druckfeder (16) in einer radialen Bohrung (18) des Deckringes (9) oder des Gehäuses (2) angeordnet ist.Radial pump (1) according to claim 4, characterized in that at least one on the pressure body (17) acting compression spring (16) in a radial bore (18) of the cover ring (9) or the housing (2) is arranged. Radialpumpe (1) nach Anspruch 4 oder 5, dadurch gekennzeichnet, dass der Druckkörper (17) eine konvexe Oberfläche aufweist.Radial pump (1) according to claim 4 or 5, characterized in that the pressure body (17) has a convex surface. Radialpumpe (1) nach Anspruch 4, dadurch gekennzeichnet, dass der Druckkörper (17) durch einen Federring (17b) gebildet ist. Radial pump (1) according to claim 4, characterized in that the pressure body (17) by a spring ring (17b) is formed. Radialpumpe (1) nach einem der Ansprüche 4 bis 7, 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.Radial pump (1) according to one of claims 4 to 7, 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. Radialpumpe (1) nach Anspruch 4 bis 7, 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.Radial pump (1) according to claim 4 to 7, characterized in that the guide surface (19) by 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. Radialpumpe (1) nach Anspruch 8 oder 9, 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 claim 8 or 9, 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. Radialpumpe (1) nach einem der Ansprüche 1 bis 10, dadurch gekennzeichnet, dass im Bereich des Deckringes (9) zumindest ein Kurzschlusskanal (23) angeordnet ist.Radial pump (1) according to one of claims 1 to 10, characterized in that in the region of the cover ring (9) at least one short-circuit channel (23) is arranged. Radialpumpe (1) nach Anspruch 11, dadurch gekennzeichnet, dass der Kurzschlusskanal (23) durch zumindest eine Ausformung im Gehäuse (2) und/oder im Deckring (9) gebildet ist.Radial pump (1) according to claim 11, characterized in that the short-circuit channel (23) by at least one formation in the housing (2) and / or in the cover ring (9) is formed. Radialpumpe (1) nach Anspruch 11, dadurch gekennzeichnet, dass der Kurzschlusskanal (23) durch den Deckring (9) aufgesteuert wird und so gestaltet ist, dass der Durchflussquerschnitt mit der Auslenkung des Deckringes (9) zunimmt.Radial pump (1) according to claim 11, characterized in that the short-circuit channel (23) is opened by the cover ring (9) and is designed so that the flow cross-section with the deflection of the cover ring (9) increases.
EP20040450193 2003-12-04 2004-10-14 Radial pump Active EP1538339B1 (en)

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EP03450273A EP1538338B1 (en) 2003-12-04 2003-12-04 Radial pump
EP03450273 2003-12-04
EP20040450193 EP1538339B1 (en) 2003-12-04 2004-10-14 Radial pump

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EP1538339B1 EP1538339B1 (en) 2006-11-22

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2009026322A1 (en) * 2007-08-22 2009-02-26 Mp Pumps Inc. Self priming centrifugal pump
WO2014086472A1 (en) * 2012-12-05 2014-06-12 Wilo Se Centrifugal pump in particular for waste water or polluted water

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2470565A (en) * 1945-10-09 1949-05-17 Ingersoll Rand Co Surge preventing device for centrifugal compressors
US2786420A (en) * 1952-03-27 1957-03-26 Stanley G Harwood Pressure controlled pump
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 (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2470565A (en) * 1945-10-09 1949-05-17 Ingersoll Rand Co Surge preventing device for centrifugal compressors
US2786420A (en) * 1952-03-27 1957-03-26 Stanley G Harwood Pressure controlled pump
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 (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2009026322A1 (en) * 2007-08-22 2009-02-26 Mp Pumps Inc. Self priming centrifugal pump
WO2014086472A1 (en) * 2012-12-05 2014-06-12 Wilo Se Centrifugal pump in particular for waste water or polluted water
CN104903584A (en) * 2012-12-05 2015-09-09 威乐欧洲股份公司 Centrifugal pump in particular for waste water or polluted water
CN104903584B (en) * 2012-12-05 2017-07-14 威乐欧洲股份公司 For waste water or the centrifugal pump of sewage

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