EP2455615A2 - Pump - Google Patents

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Publication number
EP2455615A2
EP2455615A2 EP11187213A EP11187213A EP2455615A2 EP 2455615 A2 EP2455615 A2 EP 2455615A2 EP 11187213 A EP11187213 A EP 11187213A EP 11187213 A EP11187213 A EP 11187213A EP 2455615 A2 EP2455615 A2 EP 2455615A2
Authority
EP
European Patent Office
Prior art keywords
pump
positive displacement
slide
peripheral
impeller
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
EP11187213A
Other languages
German (de)
French (fr)
Other versions
EP2455615A3 (en
EP2455615B1 (en
Inventor
Michael Baumann
Günther Beez
Holger Conrad
Oliver Gebhardt
Rüdiger Knauß
Christian Richter
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.)
Mahle International GmbH
Original Assignee
Mahle International 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
Priority claimed from DE102010044167A external-priority patent/DE102010044167A1/en
Priority claimed from DE102011079897A external-priority patent/DE102011079897A1/en
Application filed by Mahle International GmbH filed Critical Mahle International GmbH
Publication of EP2455615A2 publication Critical patent/EP2455615A2/en
Publication of EP2455615A3 publication Critical patent/EP2455615A3/en
Application granted granted Critical
Publication of EP2455615B1 publication Critical patent/EP2455615B1/en
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P5/00—Pumping cooling-air or liquid coolants
    • F01P5/10—Pumping liquid coolant; Arrangements of coolant pumps
    • 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
    • F04D15/0038—Varying behaviour or the very pump by varying the effective cross-sectional area of flow through the rotor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P11/00—Component parts, details, or accessories not provided for in, or of interest apart from, groups F01P1/00 - F01P9/00
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P7/00—Controlling of coolant flow
    • F01P7/14—Controlling of coolant flow the coolant being liquid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D5/00—Pumps with circumferential or transverse flow
    • F04D5/002—Regenerative pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2270/00—Control
    • F05D2270/60—Control system actuates means
    • F05D2270/64—Hydraulic actuators

Definitions

  • the present invention relates to a pump, in particular a coolant pump in a motor vehicle, with an impeller arranged on a pump shaft.
  • Coolant pumps are usually used in motor vehicles to control a coolant flow for cooling an internal combustion engine, the delivery rate of such coolant pumps being regulated as a function of the cooling requirement.
  • a regulation or control of the delivery rate of the coolant pump is usually carried out via electromagnetically controllable valves or couplings or other types of valves.
  • the present invention is concerned with the problem of providing for a pump, in particular for a coolant pump, an improved embodiment which is particularly compact.
  • the present invention is based on the general idea, in a pump, in particular in a coolant pump in a motor vehicle, with an arranged on a pump shaft impeller an adjustable Provide slide, which can be moved over the impeller or alternatively to move the impeller, thereby regulating a delivery rate of the pump.
  • a secondary pump is now additionally arranged on the pump shaft of the pump, for example in the form of a positive displacement pump or a peripheral pump, which serves to build up a fluid pressure controlling the slide.
  • a valve device is arranged, which separates the suction side and the pressure side from each other and thereby connects and controls the fluid pressure for adjusting the slide, which can be built up by the secondary pump or the displacement pump / peripheral pump.
  • the pump according to the invention can be used to adjust the pumping rate of the pump regulating overpressure, the rotational energy of the pump shaft of the pump, as this not only the impeller, that is the impeller, for the promotion of, for example, carries coolant, but at the same time a corresponding secondary pump in Form of a positive displacement pump / peripheral pump with a rotor set, which builds up the fluid pressure with which the slide is adjusted.
  • the suction side can be separated from the pressure side of the positive displacement pump / peripheral pump by the valve device positioned according to the invention, so that the positive displacement pump builds up a pressure which moves the slide into its closed position.
  • the valve device With increasing duration of the cold start phase, that is, with increasing warming of the internal combustion engine, the valve device can be successively opened, whereby an increasing connection between the pressure side and the suction side of the positive displacement pump / peripheral pump takes place and thereby increasingly decreases the fluid pressure generated by the positive displacement pump / peripheral pump.
  • the valve device also works like a pressure relief valve for the peripheral pump or acts to prevent damage to the pump.
  • the secondary pump / positive displacement pump / peripheral pump has a self-regulating pressure limiting device.
  • a self-regulating pressure limiting device closes from a certain of the secondary pump / positive displacement pump / peripheral pump fluid pressure, the slider, whereupon the delivery rate of the pump is reduced.
  • Such a pressure limiting device is used in particular to avoid damage that may arise at too high by the positive displacement pump or the pump itself built pressures on these themselves or on aggregates associated with it.
  • Such a pressure limiting device may, for example, at least two radially adjustable arranged on the positive displacement vane, which are biased by means of a respective spring in a promotional position against a stator.
  • the two springs coupled to the vanes ensure that the vanes are moved back radially outwards and thus back into their conveying position, in which the gap occurring between them and the stator is increasingly closed. A pressure equalization through this gap is therefore no longer possible.
  • a pump 1 which may be formed, for example, as a coolant pump in a motor vehicle, a pump shaft 2, on which rotationally fixed an impeller 3, also called pump impeller, is arranged.
  • the impeller 3 promotes by a rotational movement about an axis of the pump shaft 2, a fluid, for example. Coolant.
  • the pump 1 according to the invention has an adjustable slide 4, which can be pushed like a sleeve over the impeller 3 and thereby more or less closes an outlet 5 and regulates a delivery rate of the pump 1.
  • the slider 4 is displaceable in the axial direction of the pump 1.
  • a positive displacement pump 6 is also disposed on the pump shaft 2 .
  • valve device 7 which separates a suction side and a pressure side of the positive displacement pump 6 from each other or together and thereby controls the build-up of the positive displacement pump 6 fluid pressure for adjusting the slide 4.
  • the valve device 7 can not only have two extreme positions (open and closed), but also any intermediate positions.
  • the positive displacement pump 6 has a self-regulating pressure limiting device 8 with two radially adjustable arranged on the positive displacement pump 6 wings 9 and 9 ', which are biased by a respective spring 10 and 10' in a promotional position against a stator 11.
  • the wings 9 and 9 ' are in response to the delivery pressure of the positive displacement pump 6 radially inward and thus adjustable in a no or less strong promotional position, the adjustment of the required fluid pressure of the spring stiffness of the springs 10 and 10' depend.
  • the pump 1 functions as a coolant pump in an internal combustion engine as follows: during a cold start phase of the internal combustion engine, in which the heating of the same as quickly as possible takes place is desired, the pump 1 should promote no coolant to the engine and thereby shorten the cold start phase. During the cold start phase thus separates the valve means 7, the pressure side of the suction side of the positive displacement pump 6, whereby it builds up a fluid pressure, which then leads to the adjustment of the slide 4 in its closed position. The fluid pressure built up by the positive displacement pump 6 counteracts a spring 12 which is part of a safety device 13.
  • the valve device 7 opens a fluidic connection between the suction side and the pressure side of the positive displacement pump 6, so that the fluid pressure generated by this decreases, whereby the force exerted by the spring 12 actuating force is increasingly greater compared to that exerted by the fluid pressure and opposite force. This causes a slow adjustment of the slide 4 in its open position, whereby the pump 1 promotes coolant to the engine and thereby cools it.
  • the spring 12 is part of a safety device 13, which adjusts the slider 4 in case of failure of the positive displacement pump 6 or the valve device 7 such that the pump 1 provides the maximum delivery rate and thus the maximum cooling capacity.
  • the pump 1 With the pump 1 according to the invention, it is possible to use the rotational energy of the pump shaft 2 of the pump 1 at the same time for generating a fluid pressure adjusting the slide 4 by means of the positive displacement pump 6, so that separate pressure-generating means can be dispensed with.
  • the valve device 7 is also a simple but particularly effective control of the slide 4 on the prevailing in the positive displacement pump 6 fluid pressure possible.
  • the provided in the positive displacement pump 6 pressure limiting device 8 also ensures that no, the positive displacement pump 6 impairing or even damaging fluid pressure can be built within the same. Due to the springs 10 and 10 'while the pressure limiting device 8 operates independently and requires no additional control or regulation.
  • FIGS. 5 and 6 is on the pump shaft 2 a Peripheralpumpenrad 115 of a peripheral pump 116 for the construction of a slider 4 controlling, that is adjusting, fluid pressure.
  • a valve device 7 is provided, which separates a suction side and a pressure side of the peripheral pump 116 from each other or to each other and thereby controls the accumulatedbar of the peripheral pump 116 fluid pressure for adjusting the slide 4.
  • the valve device 7 may be formed, for example, as an electrically actuated solenoid valve (solenoid valve).
  • the valve device 7 can of course not only two Extreme (open and closed), but also any intermediate positions.
  • the pump 1 functions as a coolant pump in an internal combustion engine as follows: During the cold start phase, the valve device 7 separates the pressure side from the suction side of the peripheral pump 116, whereby it builds up a fluid pressure, which then leads to the adjustment of the slide 4 in its closed position. The fluid pressure built up by the peripheral pump 116 counteracts a spring 118, which is part of a safety device. Due to the fact that the slide 4 closes the outlet of the impeller 3, no coolant is conveyed to the internal combustion engine by the pump 1, as a result of which it is heated more quickly to operating temperature and its cold start phase is shortened. This is particularly advantageous with regard to fuel consumption and with regard to nitrogen oxide emissions.
  • valve device 7 With increasing heating of the internal combustion engine, the valve device 7 opens a fluidic connection between the suction side and the pressure side of the peripheral pump 116, so that the fluid pressure generated by this decreases. This causes a slow adjustment of the slide 4 in its open position, whereby the pump 1 promotes coolant to the engine and thereby cools it.
  • the spring 118 is part of a safety device that adjusts the slide 4 in case of failure of the peripheral pump 116 or the valve device 7 such that the pump 1 provides the maximum delivery rate and thus the maximum cooling capacity.
  • valve device 7 may comprise a valve plate 119 biased by means of a spring 118 ', the spring 118' biasing the valve plate 119 into an open position when the valve device 7 is not actuated.
  • the impeller 3 and the peripheral impeller 115 are preferably in one common fluid circuit, in particular in a common cooling circuit, integrated. In this case, the fluid delivered by the peripheral pump 116 and the fluid delivered by the pump 1 is coolant.
  • the pump 1 With the pump 1 according to the invention, it is possible to use the rotational energy of the pump shaft 2 of the pump 1 at the same time for generating a fluid pressure adjusting the slide 4 by means of the peripheral pump 116, so that separate pressure-generating devices can be dispensed with.
  • the valve device 7 is also a simple but particularly effective control of the slide 4 on the prevailing in the peripheral pump 116 fluid pressure possible. Of particular advantage is beyond that the thus designed pump 1 compact builds.
  • the valve device 7 may be an electronically / electrically controlled solenoid valve or another controlled valve.
  • the specifications of the controller can be set in the engine electronics as a map. This means that, depending on the operating state of the engine, the valve device 7 is actuated and thereby actuated.
  • Fig. 7 to 9 is another possible embodiment of the pump 1 according to the invention shown, in which the secondary pump is not explicitly drawn.
  • This is located in the secondary pump housing 200 and can be configured in any form, for example as positive displacement pump 6 or peripheral pump 116.
  • a fluid pressure is built by the secondary pump, such as an oil pump, for adjusting the slide 4 via the impeller 3 of the pump 1 is used.
  • the pump 1 has an annular piston 201, which is adjustable in an annular space 202 and coupled to the slide 4.
  • the annular piston 201 is connected via an axial seal 203 in the axial direction and over a Radial seal 204 sealed in the radial direction.
  • the valve device 7 takes over the control of the adjusting movement of the slide 4.
  • a spring 205 is provided, which in case of failure of the secondary pump, z.
  • the slider 4 adjusted such that the pump 1, the maximum delivery rate and thus the maximum cooling performance provides.
  • the shaft 2 is sealed by a seal 206 relative to the secondary pump housing 200 and mounted via a bearing 207, which may be arranged in the secondary pump housing 200.
  • annular piston 201 By the annular piston 201, a particularly uniform adjustment of the slide 4 and a space-optimized solution can be achieved.

Abstract

The pump (1) has an impeller (3) that is located on a pump shaft (2). An adjustable slider (4) is displaced over the impeller to control delivery rate of fluid pressure from a main portion. A displacement pump (6) is arranged on pump shaft to set steering fluid pressure in main portion. A valve (7) is provided to separate the suction side and pressure side of the displacement pump.

Description

Die vorliegende Erfindung betrifft eine Pumpe, insbesondere eine Kühlmittelpumpe in einem Kraftfahrzeug, mit einem auf einer Pumpenwelle angeordneten Laufrad.The present invention relates to a pump, in particular a coolant pump in a motor vehicle, with an impeller arranged on a pump shaft.

Kühlmittelpumpen dienen in Kraftfahrzeugen üblicherweise der Steuerung eines Kühlmittelstroms zur Kühlung eines Verbrennungsmotors, wobei die Förderrate derartiger Kühlmittelpumpen in Abhängigkeit des Kühlbedarfs geregelt wird. So ist insbesondere während einer Kaltstartphase des Verbrennungsmotors eine Kühlung nicht nur nicht erforderlich, sondern sogar unerwünscht, da sie die Kaltstartphase verlängert und dadurch einen erhöhten Kraftstoffverbrauch sowie erhöhte Schadstoffemissionen erzeugt. Eine Regelung bzw. Steuerung der Förderrate der Kühlmittelpumpen erfolgt dabei üblicherweise über elektromagnetisch ansteuerbare Ventile oder Kupplungen oder andersartige Ventile.Coolant pumps are usually used in motor vehicles to control a coolant flow for cooling an internal combustion engine, the delivery rate of such coolant pumps being regulated as a function of the cooling requirement. Thus, especially during a cold start phase of the engine cooling not only not required, but even undesirable because it extends the cold start phase, thereby generating increased fuel consumption and increased pollutant emissions. A regulation or control of the delivery rate of the coolant pump is usually carried out via electromagnetically controllable valves or couplings or other types of valves.

Die vorliegende Erfindung beschäftigt sich mit dem Problem, für eine Pumpe, insbesondere für eine Kühlmittelpumpe, eine verbesserte Ausführungsform anzugeben, die insbesondere kompakt baut.The present invention is concerned with the problem of providing for a pump, in particular for a coolant pump, an improved embodiment which is particularly compact.

Dieses Problem wird erfindungsgemäß durch den Gegenstand des unabhängigen Anspruchs 1 gelöst. Vorteilhafte Ausführungsformen sind Gegenstand der abhängigen Ansprüche.This problem is solved according to the invention by the subject matter of independent claim 1. Advantageous embodiments are the subject of the dependent claims.

Die vorliegende Erfindung beruht auf dem allgemeinen Gedanken, bei einer Pumpe, insbesondere bei einer Kühlmittelpumpe in einem Kraftfahrzeug, mit einem auf einer Pumpenwelle angeordneten Laufrad einen verstellbaren Schieber vorzusehen, der über das Laufrad verschoben werden kann oder alternativ das Laufrad zu verschieben und dadurch eine Förderrate der Pumpe zu regeln. Erfindungsgemäß ist nun zusätzlich auf der Pumpenwelle der Pumpe eine Sekundärpumpe beispielsweise in Form einer Verdrängerpumpe oder einer Peripheralpumpe angeordnet, die zum Aufbau eines den Schieber steuernden Fluiddrucks dient. Zwischen einer Saugseite und einer Druckseite der Verdrängerpumpe ist dabei eine Ventileinrichtung angeordnet, die die Saugseite und die Druckseite voneinander trennt bzw. miteinander verbindet und dadurch den von der Sekundärpumpe bzw. der Verdrängerpumpe/Peripheralpumpe aufbaubaren Fluiddruck zum Verstellen des Schiebers steuert. Bei der erfindungsgemäßen Pumpe kann zum Verstellen des die Förderrate der Pumpe regelnden Überdrucks die Rotationsenergie der Pumpenwelle der Pumpe genutzt werden, da dieser nicht nur das Laufrad, das heißt das Pumpenrad, zur Förderung von bspw. Kühlmittel trägt, sondern zugleich auch eine entsprechende Sekundärpumpe in Form einer Verdrängerpumpe/Peripheralpumpe mit einem Rotorsatz, die denjenigen Fluiddruck aufbaut, mit welchem der Schieber verstellt wird. Durch die erfindungsgemäß positionierte Ventileinrichtung kann somit bspw. während einer Kaltstartphase eines Verbrennungsmotors die Saugseite von der Druckseite der Verdrängerpumpe/Peripheralpumpe getrennt werden, so dass die Verdrängerpumpe einen Druck aufbaut, der den Schieber in seine Schließstellung verstellt. Bei zunehmender Dauer der Kaltstartphase, das heißt bei zunehmender Erwärmung des Verbrennungsmotors, kann die Ventileinrichtung sukzessive geöffnet werden, wodurch eine zunehmende Verbindung zwischen der Druckseite und der Saugseite der Verdrängerpumpe/Peripheralpumpe erfolgt und dadurch der von der Verdrängerpumpe/Peripheralpumpe erzeugte Fluiddruck zunehmend absinkt. Das bedeutet dass die Ventileinrichtung zusätzlich wie ein Druckbegrenzungsventil für die Peripheralpumpe arbeitet bzw. wirkt, um Schäden an den Pumpen zu vermeiden. Durch das Absinken des Fluiddrucks verstellt sich der über den Fluiddruck der Verdrängerpumpe/Peripheralpumpe gesteuerte Schieber in seine Öffnungsstellung, wodurch das Pumpenrad der Pumpe zunehmend mehr Fluid, das heißt zunehmend mehr Kühlmittel fördert und dadurch den stetig steigenden Kühlbedarf des Verbrennungsmotors befriedigt. Durch die ebenfalls auf der Pumpenwelle der Pumpe angeordnete Verdrängerpumpe/Peripheralpumpe kann somit die Rotationsenergie der Pumpenwelle zugleich zum Aufbau eines den Schieber und damit die Förderrate der Pumpe steuernden Fluiddrucks verwendet werden, so dass weitere, aufwendige und teure Stelleinrichtungen entfallen können. Für die gesamte Anmeldung soll die erwähnte Verdrängerpumpe/Peripheralpumpe eine mögliche Ausführungsform der Sekundärpumpe sein, wobei die Begriffe synonym verwendet werden können.The present invention is based on the general idea, in a pump, in particular in a coolant pump in a motor vehicle, with an arranged on a pump shaft impeller an adjustable Provide slide, which can be moved over the impeller or alternatively to move the impeller, thereby regulating a delivery rate of the pump. According to the invention, a secondary pump is now additionally arranged on the pump shaft of the pump, for example in the form of a positive displacement pump or a peripheral pump, which serves to build up a fluid pressure controlling the slide. Between a suction side and a pressure side of the positive displacement pump, a valve device is arranged, which separates the suction side and the pressure side from each other and thereby connects and controls the fluid pressure for adjusting the slide, which can be built up by the secondary pump or the displacement pump / peripheral pump. In the pump according to the invention can be used to adjust the pumping rate of the pump regulating overpressure, the rotational energy of the pump shaft of the pump, as this not only the impeller, that is the impeller, for the promotion of, for example, carries coolant, but at the same time a corresponding secondary pump in Form of a positive displacement pump / peripheral pump with a rotor set, which builds up the fluid pressure with which the slide is adjusted. Thus, for example, during a cold start phase of an internal combustion engine, the suction side can be separated from the pressure side of the positive displacement pump / peripheral pump by the valve device positioned according to the invention, so that the positive displacement pump builds up a pressure which moves the slide into its closed position. With increasing duration of the cold start phase, that is, with increasing warming of the internal combustion engine, the valve device can be successively opened, whereby an increasing connection between the pressure side and the suction side of the positive displacement pump / peripheral pump takes place and thereby increasingly decreases the fluid pressure generated by the positive displacement pump / peripheral pump. This means that the valve device also works like a pressure relief valve for the peripheral pump or acts to prevent damage to the pump. Due to the decrease in the fluid pressure is adjusted the over the fluid pressure of the positive displacement pump / peripheral pump controlled slide in its open position, whereby the impeller of the pump increasingly more fluid, that is increasingly promotes more refrigerant and thereby satisfies the ever increasing cooling demand of the engine. By also arranged on the pump shaft of the pump positive displacement pump / peripheral pump thus the rotational energy of the pump shaft can be used at the same time to build a slider and thus the flow rate of the pump controlling fluid pressure, so that more expensive and expensive adjusting devices can be omitted. For the entire application mentioned displacement / peripheral pump should be a possible embodiment of the secondary pump, the terms can be used synonymously.

Bei einer vorteilhaften Weiterbildung der erfindungsgemäßen Lösung, weist die Sekundärpumpe/Verdrängerpumpe/Peripheralpumpe eine selbstregelnde Druckbegrenzungseinrichtung auf. Eine derartige selbstregelnde Druckbegrenzungseinrichtung schließt ab einem gewissen von der Sekundärpumpe/Verdrängerpumpe/Peripheralpumpe aufgebauten Fluiddruck den Schieber, woraufhin die Förderrate der Pumpe reduziert wird. Eine derartige Druckbegrenzungseinrichtung dient insbesondere zur Vermeidung von Schäden, die bei zu hohen durch die Verdrängerpumpe oder die Pumpe selbst aufgebauten Drücken an diesen selbst oder an damit verbundenen Aggregaten entstehen können. Eine derartige Druckbegrenzungseinrichtung kann bspw. zumindest zwei radial verstellbar an der Verdrängerpumpe angeordnete Flügel aufweisen, die mittels jeweils einer Feder in eine fördernde Stellung gegen einen Stator vorgespannt sind. Bei einem in der Verdrängerpumpe herrschenden Fluiddruck unterhalb eines kritischen Wertes befinden sich somit die beiden Flügel aufgrund der darauf wirkenden Federn in ihrer ausgefahrenen und damit fördernden Stellung, wogegen die Flügel bei steigendem Fluiddruck innerhalb der Verdrängerpumpe entgegen der jeweiligen Federkraft radial nach innen gedrückt werden, wodurch ein Spalt zwischen diesem und einem außenliegenden Stator entsteht, durch den das zu fördernde Fluid fließt und durch den der innerhalb der Verdrängerpumpe herrschende Fluidausgangsdruck begrenzt werden kann. Je stärker der Fluiddruck innerhalb der Verdrängerpumpe ist, desto mehr werden die beiden Flügel nach innen gedrückt und damit die Förderrate der Verdrängerpumpe reduziert. Bei nachlassendem Fluiddruck innerhalb der Verdrängerpumpe sorgen die beiden mit den Flügeln gekoppelten Federn dafür, dass die Flügel wieder nach radial außen und damit in ihre fördernde Stellung zurück verstellt werden, in welcher der zwischen diesen und dem Stator auftretende Spalt zunehmend geschlossen wird. Ein Druckausgleich durch diesen Spalt ist somit nicht mehr möglich.In an advantageous development of the solution according to the invention, the secondary pump / positive displacement pump / peripheral pump has a self-regulating pressure limiting device. Such a self-regulating pressure limiting device closes from a certain of the secondary pump / positive displacement pump / peripheral pump fluid pressure, the slider, whereupon the delivery rate of the pump is reduced. Such a pressure limiting device is used in particular to avoid damage that may arise at too high by the positive displacement pump or the pump itself built pressures on these themselves or on aggregates associated with it. Such a pressure limiting device may, for example, at least two radially adjustable arranged on the positive displacement vane, which are biased by means of a respective spring in a promotional position against a stator. At a prevailing in the positive displacement pump fluid pressure below a critical value thus are the two wings due to the springs acting thereon in its extended and thus promoting position, whereas the wings with increasing fluid pressure within the Positive displacement pump are pressed against the respective spring force radially inwardly, whereby a gap between this and an outer stator is formed, through which flows the fluid to be delivered and by the prevailing within the positive displacement fluid outlet pressure can be limited. The stronger the fluid pressure within the positive displacement pump, the more the two vanes are pressed inwards, thus reducing the delivery rate of the positive displacement pump. With decreasing fluid pressure within the positive displacement pump, the two springs coupled to the vanes ensure that the vanes are moved back radially outwards and thus back into their conveying position, in which the gap occurring between them and the stator is increasingly closed. A pressure equalization through this gap is therefore no longer possible.

Weitere wichtige Merkmale und Vorteile der Erfindung ergeben sich aus den Unteransprüchen, aus den Zeichnungen und aus der zugehörigen Figurenbeschreibung anhand der Zeichnungen.Other important features and advantages of the invention will become apparent from the dependent claims, from the drawings and from the associated figure description with reference to the drawings.

Es versteht sich, dass die vorstehend genannten und die nachstehend noch zu erläuternden Merkmale nicht nur in der jeweils angegebenen Kombination, sondern auch in anderen Kombinationen oder in Alleinstellung verwendbar sind, ohne den Rahmen der vorliegenden Erfindung zu verlassen.It is understood that the features mentioned above and those yet to be explained below can be used not only in the particular combination given, but also in other combinations or in isolation, without departing from the scope of the present invention.

Bevorzugte Ausführungsbeispiele der Erfindung sind in den Zeichnungen dargestellt und werden in der nachfolgenden Beschreibung näher erläutert, wobei sich gleiche Bezugszeichen auf gleiche oder ähnliche oder funktional gleiche Bauteile beziehen.Preferred embodiments of the invention are illustrated in the drawings and will be described in more detail in the following description, wherein like reference numerals refer to the same or similar or functionally identical components.

Dabei zeigen, jeweils schematisch,

Fig. 1
eine Schnittdarstellung durch eine erfindungsgemäße Pumpe,
Fig. 2a
eine Schnittdarstellung wie in Fig. 1, jedoch aus einer anderen Perspektive und mit geöffnetem Schieber,
Fig. 2b
eine Darstellung wie in Fig. 2a, jedoch bei geschlossenem Schieber,
Fig. 3a,
b eine Verdrängerpumpe aus unterschiedlichen Ansichten,
Fig. 4
eine Detaildarstellung einer Druckbegrenzungseinrichtung der Verdrängerpumpe,
Fig. 5
eine Schnittdarstellung durch eine erfindungsgemäße Pumpe mit geöffnetem Schieber,
Fig. 6
eine Schnittdarstellung wie in Fig. 5, jedoch bei geschlossenem Schieber,
Fig. 7
eine weitere mögliche Ausführungsform der erfindungsgemäßen Pumpe,
Fig. 8
die Pumpe aus Fig. 7 bei voller Förderleistung,
Fig. 9
die Pumpe aus Fig. 7 ohne Förderleistung.
Show, in each case schematically,
Fig. 1
a sectional view through a pump according to the invention,
Fig. 2a
a sectional view as in Fig. 1 but from a different perspective and with the slider open,
Fig. 2b
a representation like in Fig. 2a , but with the slider closed,
Fig. 3a,
b a positive displacement pump from different views,
Fig. 4
a detailed representation of a pressure limiting device of the positive displacement pump,
Fig. 5
a sectional view through a pump according to the invention with open slide,
Fig. 6
a sectional view as in Fig. 5 , but with the slider closed,
Fig. 7
another possible embodiment of the pump according to the invention,
Fig. 8
the pump off Fig. 7 at full capacity,
Fig. 9
the pump off Fig. 7 without delivery.

Entsprechend der Fig. 1, weist eine Pumpe 1, die bspw. als Kühlmittelpumpe in einem Kraftfahrzeug ausgebildet sein kann, einer Pumpenwelle 2 auf, auf welchem drehfest ein Laufrad 3, auch Pumpenrad genannt, angeordnet ist. Das Laufrad 3 fördert durch eine Drehbewegung um eine Achse der Pumpenwelle 2 ein Fluid, bspw. Kühlmittel. Darüber hinaus weist die erfindungsgemäße Pumpe 1 einen verstellbaren Schieber 4 auf, der hülsenartig über das Laufrad 3 geschoben werden kann und dadurch einen Auslass 5 mehr oder weniger verschließt und eine Förderrate der Pumpe 1 regelt. Der Schieber 4 ist dabei in Axialrichtung der Pumpe 1 verschiebbar. Ebenfalls auf der Pumpenwelle 2 angeordnet ist eine Verdrängerpumpe 6 (vgl. auch die Fig. 2 bis 4) zum Aufbau eines den Schieber 4 steuernden, das heißt verstellenden, Fluiddrucks. Zusätzlich ist eine Ventileinrichtung 7 vorgesehen, die eine Saugseite und eine Druckseite der Verdrängerpumpe 6 voneinander trennt oder miteinander verbindet und dadurch den von der Verdrängerpumpe 6 aufbaubaren Fluiddruck zum Verstellen des Schiebers 4 steuert. Die Ventileinrichtung 7 kann dabei selbstverständlich nicht nur zwei Extremalstellungen (offen und zu) aufweisen, sondern auch beliebige Zwischenstellungen.According to the Fig. 1 , A pump 1, which may be formed, for example, as a coolant pump in a motor vehicle, a pump shaft 2, on which rotationally fixed an impeller 3, also called pump impeller, is arranged. The impeller 3 promotes by a rotational movement about an axis of the pump shaft 2, a fluid, for example. Coolant. In addition, the pump 1 according to the invention has an adjustable slide 4, which can be pushed like a sleeve over the impeller 3 and thereby more or less closes an outlet 5 and regulates a delivery rate of the pump 1. The slider 4 is displaceable in the axial direction of the pump 1. Also disposed on the pump shaft 2 is a positive displacement pump 6 (see also FIGS Fig. 2 to 4 ) to build a slider 4 controlling, that is adjusting, fluid pressure. In addition, a valve device 7 is provided, which separates a suction side and a pressure side of the positive displacement pump 6 from each other or together and thereby controls the build-up of the positive displacement pump 6 fluid pressure for adjusting the slide 4. Of course, the valve device 7 can not only have two extreme positions (open and closed), but also any intermediate positions.

Betrachtet man die Fig. 2 bis 4, so kann man erkennen, dass die Verdrängerpumpe 6 eine selbstregelnde Druckbegrenzungseinrichtung 8 aufweist mit zwei radial verstellbar an der Verdrängerpumpe 6 angeordneten Flügeln 9 und 9', die mittels jeweils einer Feder 10 und 10' in eine fördernde Stellung gegen einen Stator 11 vorgespannt sind. Die Flügel 9 und 9' sind dabei in Abhängigkeit des Förderdrucks der Verdrängerpumpe 6 nach radial innen und damit in eine nicht oder nur weniger stark fördernde Stellung verstellbar, wobei die Verstellbewegung der dafür erforderliche Fluiddruck von der Federsteifigkeit der Federn 10 und 10' abhängen.Looking at the Fig. 2 to 4 , it can be seen that the positive displacement pump 6 has a self-regulating pressure limiting device 8 with two radially adjustable arranged on the positive displacement pump 6 wings 9 and 9 ', which are biased by a respective spring 10 and 10' in a promotional position against a stator 11. The wings 9 and 9 'are in response to the delivery pressure of the positive displacement pump 6 radially inward and thus adjustable in a no or less strong promotional position, the adjustment of the required fluid pressure of the spring stiffness of the springs 10 and 10' depend.

Die erfindungsgemäße Pumpe 1 funktioniert dabei als Kühlmittelpumpe bei einem Verbrennungsmotor wie folgt: Während einer Kaltstartphase des Verbrennungsmotors, bei dem eine möglichst rasche Erwärmung desselben erwünscht wird, soll die Pumpe 1 kein Kühlmittel zum Verbrennungsmotor fördern und dadurch die Kaltstartphase verkürzen. Während der Kaltstartphase trennt somit die Ventileinrichtung 7 die Druckseite von der Saugseite der Verdrängerpumpe 6, wodurch diese einen Fluiddruck aufbaut, der dann zum Verstellen des Schiebers 4 in seine geschlossene Stellung führt. Der durch die Verdrängerpumpe 6 aufgebaute Fluiddruck wirkt dabei einer Feder 12, die Bestandteil einer Sicherheitseinrichtung 13 ist, entgegen. Durch den Umstand, dass der Schieber 4 den Auslass 5 des Pumpenrads 3 verschließt, wird von der Pumpe 1 kein Kühlmittel zum Verbrennungsmotor gefördert, wodurch dieser schneller auf Betriebstemperatur erwärmt und dessen Kaltstartphase verkürzt wird. Dies ist insbesondere im Hinblick auf einen Kraftstoffverbrauch und im Hinblick auf Stickoxidemissionen von großem Vorteil. Mit zunehmender Erwärmung des Verbrennungsmotors öffnet die Ventileinrichtung 7 eine fluidtechnische Verbindung zwischen der Saugseite und der Druckseite der Verdrängerpumpe 6, so dass der von dieser erzeugte Fluiddruck absinkt, wodurch die von der Feder 12 ausgeübte Stellkraft zunehmend größer wird im Vergleich zu der vom Fluiddruck ausgeübten und entgegengesetzten Stellkraft. Dies bewirkt ein langsames Verstellen des Schiebers 4 in dessen Öffnungsstellung, wodurch die Pumpe 1 Kühlmittel zum Verbrennungsmotor fördert und diesen dadurch kühlt. Die Feder 12 ist dabei Bestandteil einer Sicherheitseinrichtung 13, die beim Ausfall der Verdrängerpumpe 6 oder der Ventileinrichtung 7 den Schieber 4 derart verstellt, dass die Pumpe 1 die maximale Förderrate und damit die maximale Kühlleistung erbringt.The pump 1 according to the invention functions as a coolant pump in an internal combustion engine as follows: during a cold start phase of the internal combustion engine, in which the heating of the same as quickly as possible takes place is desired, the pump 1 should promote no coolant to the engine and thereby shorten the cold start phase. During the cold start phase thus separates the valve means 7, the pressure side of the suction side of the positive displacement pump 6, whereby it builds up a fluid pressure, which then leads to the adjustment of the slide 4 in its closed position. The fluid pressure built up by the positive displacement pump 6 counteracts a spring 12 which is part of a safety device 13. Due to the fact that the slide 4 closes the outlet 5 of the pump impeller 3, no coolant is conveyed to the internal combustion engine by the pump 1, as a result of which it is heated more quickly to operating temperature and its cold start phase is shortened. This is particularly advantageous with regard to fuel consumption and with regard to nitrogen oxide emissions. With increasing warming of the internal combustion engine, the valve device 7 opens a fluidic connection between the suction side and the pressure side of the positive displacement pump 6, so that the fluid pressure generated by this decreases, whereby the force exerted by the spring 12 actuating force is increasingly greater compared to that exerted by the fluid pressure and opposite force. This causes a slow adjustment of the slide 4 in its open position, whereby the pump 1 promotes coolant to the engine and thereby cools it. The spring 12 is part of a safety device 13, which adjusts the slider 4 in case of failure of the positive displacement pump 6 or the valve device 7 such that the pump 1 provides the maximum delivery rate and thus the maximum cooling capacity.

Bei Verdrängerpumpen 6 ist die Begrenzung eines tolerierbaren Fluiddrucks innerhalb der Verdrängerpumpe 6 erforderlich, da ansonsten der Druck stetig ansteigen und zu Schäden an der Verdrängerpumpe 6 bzw. der Pumpe 1 führen kann. Bei zunehmendem Fluiddruck innerhalb der Verdrängerpumpe 6 werden nun die beiden Flügel 9 und 9' entgegen der von den zugehörigen Federn 10, 10' ausgeübten Federkraft nach radial innen verstellt, wodurch sich zwischen den Flügeln 9 und 9' und dem außenliegenden Stator ein Spalt einstellt, durch welchen ein Druckausgleich möglich ist und dadurch Fluiddruck innerhalb der Verdrängerpumpe 6 begrenzt wird. Die Druckbegrenzungseinrichtung 8 wirkt dabei selbstregulierend und bedarf keiner zusätzlichen Steuerungs- bzw. Regelungselemente.In positive displacement pumps 6, the limitation of a tolerable fluid pressure within the positive displacement pump 6 is required, since otherwise the pressure may increase steadily and may lead to damage to the positive displacement pump 6 or the pump 1. With increasing fluid pressure within the positive displacement pump 6 are now the two wings 9 and 9 'opposite to that of the associated springs 10, 10' applied spring force radially inwardly adjusted, whereby a gap between the wings 9 and 9 'and the outer stator, through which a pressure compensation is possible and thereby fluid pressure within the positive displacement pump 6 is limited. The pressure limiting device 8 acts self-regulating and requires no additional control or regulating elements.

Mit der erfindungsgemäßen Pumpe 1 ist es möglich, die Rotationsenergie der Pumpenwelle 2 der Pumpe 1 zugleich zur Erzeugung eines den Schieber 4 verstellenden Fluiddrucks mittels der Verdrängerpumpe 6 zu nutzen, so dass separate druckerzeugende Einrichtungen entfallen können. Durch die Ventileinrichtung 7 ist zudem eine einfache aber besonders wirkungsvolle Steuerung des Schiebers 4 über den in der Verdrängerpumpe 6 herrschenden Fluiddruck möglich. Die in der Verdrängerpumpe 6 vorgesehene Druckbegrenzungseinrichtung 8 gewährleistet darüber hinaus, dass kein, die Verdrängerpumpe 6 beeinträchtigender oder gar beschädigender Fluiddruck innerhalb derselben aufgebaut werden kann. Aufgrund der Federn 10 und 10' arbeitet dabei die Druckbegrenzungseinrichtung 8 autark und bedarf keiner zusätzlichen Steuerung bzw. Regelung.With the pump 1 according to the invention, it is possible to use the rotational energy of the pump shaft 2 of the pump 1 at the same time for generating a fluid pressure adjusting the slide 4 by means of the positive displacement pump 6, so that separate pressure-generating means can be dispensed with. By the valve device 7 is also a simple but particularly effective control of the slide 4 on the prevailing in the positive displacement pump 6 fluid pressure possible. The provided in the positive displacement pump 6 pressure limiting device 8 also ensures that no, the positive displacement pump 6 impairing or even damaging fluid pressure can be built within the same. Due to the springs 10 and 10 'while the pressure limiting device 8 operates independently and requires no additional control or regulation.

Entsprechend den Fig. 5 und 6 ist auf der Pumpenwelle 2 ein Peripheralpumpenrad 115 einer Peripheralpumpe 116 zum Aufbau eines den Schieber 4 steuernden, das heißt verstellenden, Fluiddrucks. Zusätzlich ist eine Ventileinrichtung 7 vorgesehen, die eine Saugseite und eine Druckseite der Peripheralpumpe 116 voneinander trennt oder miteinander verbindet und dadurch den von der Peripheralpumpe 116 aufbaubaren Fluiddruck zum Verstellen des Schiebers 4 steuert. Die Ventileinrichtung 7 kann dabei bspw. als elektrisch betätigbares Magnetventil (Solenoidventil) ausgebildet sein. Die Ventileinrichtung 7 kann dabei selbstverständlich nicht nur zwei Extremalstellungen (offen und zu) aufweisen, sondern auch beliebige Zwischenstellungen.According to the FIGS. 5 and 6 is on the pump shaft 2 a Peripheralpumpenrad 115 of a peripheral pump 116 for the construction of a slider 4 controlling, that is adjusting, fluid pressure. In addition, a valve device 7 is provided, which separates a suction side and a pressure side of the peripheral pump 116 from each other or to each other and thereby controls the aufbaubar of the peripheral pump 116 fluid pressure for adjusting the slide 4. The valve device 7 may be formed, for example, as an electrically actuated solenoid valve (solenoid valve). The valve device 7 can of course not only two Extreme (open and closed), but also any intermediate positions.

Die erfindungsgemäße Pumpe 1 funktioniert dabei als Kühlmittelpumpe bei einem Verbrennungsmotor wie folgt: Während der Kaltstartphase trennt die Ventileinrichtung 7 die Druckseite von der Saugseite der Peripheralpumpe 116, wodurch diese einen Fluiddruck aufbaut, der dann zum Verstellen des Schiebers 4 in seine geschlossene Stellung führt. Der durch die Peripheralpumpe 116 aufgebaute Fluiddruck wirkt dabei einer Feder 118, die Bestandteil einer Sicherheitseinrichtung ist, entgegen. Durch den Umstand, dass der Schieber 4 den Auslass des Laufrads 3 verschließt, wird von der Pumpe 1 kein Kühlmittel zum Verbrennungsmotor gefördert, wodurch dieser schneller auf Betriebstemperatur erwärmt und dessen Kaltstartphase verkürzt wird. Dies ist insbesondere im Hinblick auf einen Kraftstoffverbrauch und im Hinblick auf Stickoxidemissionen von großem Vorteil. Mit zunehmender Erwärmung des Verbrennungsmotors öffnet die Ventileinrichtung 7 eine fluidtechnische Verbindung zwischen der Saugseite und der Druckseite der Peripheralpumpe 116, so dass der von dieser erzeugte Fluiddruck absinkt. Dies bewirkt ein langsames Verstellen des Schiebers 4 in dessen Öffnungsstellung, wodurch die Pumpe 1 Kühlmittel zum Verbrennungsmotor fördert und diesen dadurch kühlt. Die Feder 118 ist dabei Bestandteil einer Sicherheitseinrichtung, die beim Ausfall der Peripheralpumpe 116 oder der Ventileinrichtung 7 den Schieber 4 derart verstellt, dass die Pumpe 1 die maximale Förderrate und damit die maximale Kühlleistung erbringt.The pump 1 according to the invention functions as a coolant pump in an internal combustion engine as follows: During the cold start phase, the valve device 7 separates the pressure side from the suction side of the peripheral pump 116, whereby it builds up a fluid pressure, which then leads to the adjustment of the slide 4 in its closed position. The fluid pressure built up by the peripheral pump 116 counteracts a spring 118, which is part of a safety device. Due to the fact that the slide 4 closes the outlet of the impeller 3, no coolant is conveyed to the internal combustion engine by the pump 1, as a result of which it is heated more quickly to operating temperature and its cold start phase is shortened. This is particularly advantageous with regard to fuel consumption and with regard to nitrogen oxide emissions. With increasing heating of the internal combustion engine, the valve device 7 opens a fluidic connection between the suction side and the pressure side of the peripheral pump 116, so that the fluid pressure generated by this decreases. This causes a slow adjustment of the slide 4 in its open position, whereby the pump 1 promotes coolant to the engine and thereby cools it. The spring 118 is part of a safety device that adjusts the slide 4 in case of failure of the peripheral pump 116 or the valve device 7 such that the pump 1 provides the maximum delivery rate and thus the maximum cooling capacity.

Zusätzlich kann die Ventileinrichtung 7 einen mittels einer Feder 118' vorgespannten Ventilteller 119 aufweisen, wobei die Feder 118' bei unbetätigter Ventileinrichtung 7 den Ventilteller 119 in eine Öffnungsstellung vorspannt. Das Laufrad 3 und das Peripheralpumpenrad 115 sind vorzugsweise in einen gemeinsamen Fluidkreislauf, insbesondere in einen gemeinsamen Kühlkreislauf, eingebunden. In diesem Fall ist das von der Peripheralpumpe 116 geförderte Fluid und das von der Pumpe 1 geförderte Fluid Kühlmittel.In addition, the valve device 7 may comprise a valve plate 119 biased by means of a spring 118 ', the spring 118' biasing the valve plate 119 into an open position when the valve device 7 is not actuated. The impeller 3 and the peripheral impeller 115 are preferably in one common fluid circuit, in particular in a common cooling circuit, integrated. In this case, the fluid delivered by the peripheral pump 116 and the fluid delivered by the pump 1 is coolant.

Mit der erfindungsgemäßen Pumpe 1 ist es möglich, die Rotationsenergie der Pumpenwelle 2 der Pumpe 1 zugleich zur Erzeugung eines den Schieber 4 verstellenden Fluiddrucks mittels der Peripheralpumpe 116 zu nutzen, so dass separate druckerzeugende Einrichtungen entfallen können. Durch die Ventileinrichtung 7 ist zudem eine einfache aber besonders wirkungsvolle Steuerung des Schiebers 4 über den in der Peripheralpumpe 116 herrschenden Fluiddruck möglich. Von besonderem Vorteil ist darüber hinaus, dass die derart konzipierte Pumpe 1 kompakt baut.With the pump 1 according to the invention, it is possible to use the rotational energy of the pump shaft 2 of the pump 1 at the same time for generating a fluid pressure adjusting the slide 4 by means of the peripheral pump 116, so that separate pressure-generating devices can be dispensed with. By the valve device 7 is also a simple but particularly effective control of the slide 4 on the prevailing in the peripheral pump 116 fluid pressure possible. Of particular advantage is beyond that the thus designed pump 1 compact builds.

Die Ventileinrichtung 7 kann ein elektronisch/elektrisch gesteuertes Magnetventil oder ein anderes gesteuertes Ventil sein. Die Vorgaben der Steuerung können in der Motorelektronik als Kennfeld fest gelegt sein. Das bedeutet, dass je nach Betriebszustand des Motors die Ventileinrichtung 7 angesteuert wird und dadurch betätigt wird.The valve device 7 may be an electronically / electrically controlled solenoid valve or another controlled valve. The specifications of the controller can be set in the engine electronics as a map. This means that, depending on the operating state of the engine, the valve device 7 is actuated and thereby actuated.

In den Fig. 7 bis 9 ist eine weitere mögliche Ausführungsform der erfindungsgemäßen Pumpe 1 dargestellt, bei welcher die Sekundärpumpe jedoch nicht explizit eingezeichnet ist. Diese befindet sich im Sekundärpumpengehäuse 200 und kann in beliebiger Form ausgestaltet sein, beispielsweise als Verdrängerpumpe 6 oder als Peripheralpumpe 116. Auch bei dieser Pumpe 1 wird durch die Sekundärpumpe, beispielsweise eine Ölpumpe, ein Fluiddruck aufgebaut, der zum Verstellen des Schiebers 4 über das Laufrad 3 der Pumpe 1 genutzt wird. Im vorliegenden Fall weist die Pumpe 1 einen Ringkolben 201 auf, der in einem Ringraum 202 verstellbar und mit dem Schieber 4 gekoppelt ist. Der Ringkolben 201 ist über eine Axialdichtung 203 in Axialrichtung und über eine Radialdichtung 204 in Radialrichtung abgedichtet. Die Ventileinrichtung 7 übernimmt wiederum die Steuerung der Verstellbewegung des Schiebers 4. Als Sicherheitseinrichtung ist wiederum eine Feder 205 vorgesehen, die beim Ausfall der Sekundärpumpe, z. B. der Peripheralpumpe 116, oder der Ventileinrichtung 7 den Schieber 4 derart verstellt, dass die Pumpe 1 die maximale Förderrate und damit die maximale Kühlleistung erbringt. Die Welle 2 wird über eine Dichtung 206 gegenüber dem Sekundärpumpengehäuse 200 abgedichtet und über ein Lager 207, welches im Sekundärpumpengehäuse 200 angeordnet sein kann gelagert.In the Fig. 7 to 9 is another possible embodiment of the pump 1 according to the invention shown, in which the secondary pump is not explicitly drawn. This is located in the secondary pump housing 200 and can be configured in any form, for example as positive displacement pump 6 or peripheral pump 116. Also in this pump 1, a fluid pressure is built by the secondary pump, such as an oil pump, for adjusting the slide 4 via the impeller 3 of the pump 1 is used. In the present case, the pump 1 has an annular piston 201, which is adjustable in an annular space 202 and coupled to the slide 4. The annular piston 201 is connected via an axial seal 203 in the axial direction and over a Radial seal 204 sealed in the radial direction. The valve device 7 in turn takes over the control of the adjusting movement of the slide 4. As a safety device, in turn, a spring 205 is provided, which in case of failure of the secondary pump, z. As the peripheral pump 116, or the valve device 7, the slider 4 adjusted such that the pump 1, the maximum delivery rate and thus the maximum cooling performance provides. The shaft 2 is sealed by a seal 206 relative to the secondary pump housing 200 and mounted via a bearing 207, which may be arranged in the secondary pump housing 200.

Durch den Ringkolben 201 kann eine besonders gleichmäßige Verstellung des Schiebers 4 und eine bauraumoptimierte Lösung erreicht werden.By the annular piston 201, a particularly uniform adjustment of the slide 4 and a space-optimized solution can be achieved.

Claims (14)

Pumpe (1), insbesondere eine Kühlmittelpumpe in einem Kraftfahrzeug, mit - einem auf einer Pumpenwelle (2) angeordneten Laufrad (3,113), - einem verstellbaren Schieber (4), der über das Laufrad (3,113) verschoben werden kann und dadurch eine Förderrate der Pumpe (1) regelt, - einer ebenfalls auf der Pumpenwelle (2) angeordneten Sekundärpumpe, vorzugsweise eine Verdrängerpumpe (6)/ Peripheralpumpe (116), zum Aufbau eines den Schieber (4) steuernden Fluiddrucks, - mit einer Ventileinrichtung (7), die eine Saugseite und eine Druckseite der Sekundärpumpe, vorzugsweise der Verdrängerpumpe (6)/ Peripheralpumpe (116), voneinander trennt oder verbindet und dadurch den von der Sekundärpumpe aufbaubaren Fluiddruck zum Verstellen des Schiebers (4) steuert. Pump (1), in particular a coolant pump in a motor vehicle, with an impeller (3, 11) arranged on a pump shaft (2), - An adjustable slide (4), which can be moved over the impeller (3,113) and thereby regulates a delivery rate of the pump (1), a secondary pump likewise arranged on the pump shaft (2), preferably a positive-displacement pump (6) / peripheral pump (116), for establishing a fluid pressure controlling the slide (4), - With a valve device (7) which separates a suction side and a pressure side of the secondary pump, preferably the positive displacement pump (6) / peripheral pump (116) from each other and thereby controls the aufbaubar of the secondary pump fluid pressure for adjusting the slide (4). Pumpe nach Anspruch 1,
dadurch gekennzeichnet, dass
die Ventileinrichtung (7) ein elektrisch betätigbares Magnetventil aufweist.Pump according to claim 1,
characterized in that
the valve device (7) has an electrically actuated solenoid valve. Pumpe nach Anspruch 1 oder 2,
dadurch gekennzeichnet, dass
die Sekundärpumpe/Verdrängerpumpe (6) eine selbst regelnde Druckbegrenzungseinrichtung (8) aufweist.Pump according to claim 1 or 2,
characterized in that
the secondary pump / positive displacement pump (6) has a self-regulating pressure limiting device (8). Pumpe nach Anspruch 3,
dadurch gekennzeichnet, dass
die Druckbegrenzungseinrichtung (8) zumindest zwei radial verstellbar an der Sekundärpumpe/Verdrängerpumpe (6) angeordnete Flügel (9,9') aufweist, die mittels jeweils einer Feder (10,10') in eine fördernde Stellung gegen einen Stator (11) vorgespannt sind.Pump according to claim 3,
characterized in that
the pressure limiting device (8) at least two radially adjustable on the secondary pump / positive displacement pump (6) arranged wings (9,9 ') which are biased by means of a respective spring (10,10') in a conveying position against a stator (11) , Pumpe nach Anspruch 4,
dadurch gekennzeichnet, dass
die Flügel (9,9') in Abhängigkeit des Förderdrucks der Sekundärpumpe/ Verdrängerpumpe (6) nach radial innen und damit in eine nicht oder weniger stark fördernde Stellung verstellbar sind.Pump according to claim 4,
characterized in that
the wings (9,9 ') in dependence of the delivery pressure of the secondary pump / positive displacement pump (6) radially inward and thus are adjustable in a non or less promotional position. Pumpe nach einem der Ansprüche 1 bis 5,
dadurch gekennzeichnet, dass
das von der Sekundärpumpe/Verdrängerpumpe/Peripheralpumpe (6,116) geförderte Fluid und das von der Pumpe (1) geförderte Fluid Kühlmittel ist.Pump according to one of claims 1 to 5,
characterized in that
that of the secondary pump / positive displacement pump / peripheral pump (6.116) funded fluid and the funded by the pump (1) fluid is coolant. Pumpe nach einem der Ansprüche 1 bis 6,
dadurch gekennzeichnet, dass
eine Federeinrichtung (118) bzw. eine Sicherheitseinrichtung (13) vorgesehen ist, die beim Ausfall der Sekundärpumpe/Verdrängerpumpe/ Peripheralpumpe (6,116) den Schieber (4) derart verstellt, dass die Pumpe (1) die maximale Förderrate erbringt.Pump according to one of claims 1 to 6,
characterized in that
a spring device (118) or a safety device (13) is provided which, in the event of failure of the secondary pump / displacement pump / peripheral pump (6,116) adjusts the slide (4) such that the pump (1) provides the maximum delivery rate. Pumpe nach einem der vorhergehenden Ansprüche,
dadurch gekennzeichnet, dass
der verstellbare Schieber (4) als Verstellhülse ausgebildet ist, die in Axialrichtung über das Laufrad (3) verschiebbar ist.Pump according to one of the preceding claims,
characterized in that
the adjustable slide (4) is designed as an adjusting sleeve, which is displaceable in the axial direction over the impeller (3). Pumpe nach Anspruch 1,
dadurch gekennzeichnet, dass
die Ventileinrichtung (7) einen mittels einer Feder (118') vorgespannten Ventilteller (119) aufweist, wobei die Feder (118') bei unbetätigter Ventileinrichtung (7) den Ventilteller (119) in eine Öffnungsstellung vorspannt.Pump according to claim 1,
characterized in that
the valve device (7) has a valve plate (119) prestressed by means of a spring (118 '), wherein the spring (118') biases the valve plate (119) into an open position when the valve device (7) is not actuated. Pumpe nach Anspruch 1 oder 9,
dadurch gekennzeichnet, dass
das Laufrad (113) und ein Peripheralpumpenrad (115) der Peripheralpumpe (116) in einen gemeinsamen Fluidkreislauf eingebunden sind.Pump according to claim 1 or 9,
characterized in that
the impeller (113) and a Peripheralpumpenrad (115) of the peripheral pump (116) are integrated into a common fluid circuit. Pumpe nach einem der Ansprüche 1 bis 10,
dadurch gekennzeichnet, dass
die Pumpe (1) einen Ringkolben (201) auf, der in einem Ringraum (202) verstellbar und mit dem Schieber (4) gekoppelt ist.Pump according to one of claims 1 to 10,
characterized in that
the pump (1) has an annular piston (201) which is adjustable in an annular space (202) and coupled to the slide (4). Pumpe nach Anspruch 11,
dadurch gekennzeichnet, dass
der Ringkolben (201) über eine Axialdichtung (203) in Axialrichtung und über eine Radialdichtung (204) in Radialrichtung abgedichtet ist.Pump according to claim 11,
characterized in that
the annular piston (201) via an axial seal (203) in the axial direction and via a radial seal (204) is sealed in the radial direction. Pumpe nach Anspruch 12,
dadurch gekennzeichnet, dass
die Welle (2) über eine Dichtung (206) gegenüber einem Sekundärpumpengehäuse (200) abgedichtet ist, und/oder über ein Lager (207), welches im Sekundärpumpengehäuse (200) angeordnet ist, gelagert ist.Pump according to claim 12,
characterized in that
the shaft (2) is sealed off from a secondary pump housing (200) via a seal (206), and / or via a bearing (207), which is arranged in the secondary pump housing (200) is stored. Pumpe nach einem der Ansprüche 1 bis 13,
dadurch gekennzeichnet, dass
die Pumpe (1) als Kühlmittelpumpe zum Umwälzen eines Kühlmittels für einen Verbrennungsmotor eines Kraftfahrzeugs ausgebildet ist.Pump according to one of claims 1 to 13,
characterized in that
the pump (1) is designed as a coolant pump for circulating a coolant for an internal combustion engine of a motor vehicle.
EP11187213.1A 2010-11-19 2011-10-31 Pump Not-in-force EP2455615B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102010044167A DE102010044167A1 (en) 2010-11-19 2010-11-19 Coolant pump mounted in motor vehicle, has valve device that is provided to disconnect suction side and pressure side of displacement pump which is connected to slider, for adjusting fluid pressure
DE102011079897A DE102011079897A1 (en) 2011-07-27 2011-07-27 Pump, particularly coolant pump, for cooling internal combustion engine of motor vehicle, has impeller arranged on pump shaft, where adjustable slider is displaced over impeller and regulates flow rate of pump

Publications (3)

Publication Number Publication Date
EP2455615A2 true EP2455615A2 (en) 2012-05-23
EP2455615A3 EP2455615A3 (en) 2014-04-09
EP2455615B1 EP2455615B1 (en) 2017-08-16

Family

ID=44862793

Family Applications (1)

Application Number Title Priority Date Filing Date
EP11187213.1A Not-in-force EP2455615B1 (en) 2010-11-19 2011-10-31 Pump

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EP (1) EP2455615B1 (en)
KR (1) KR101819750B1 (en)
CN (1) CN102477996B (en)

Cited By (3)

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Publication number Priority date Publication date Assignee Title
US20120204818A1 (en) * 2011-02-15 2012-08-16 Schwabische Huttenwerke Automotive Gmbh Coolant pump which exhibits an adjustable delivery volume
WO2017076645A1 (en) * 2015-11-06 2017-05-11 Pierburg Gmbh Coolant pump for an internal combustion engine
EP3290713A1 (en) * 2016-09-06 2018-03-07 Pierburg GmbH Coolant pump for the automotive sector and a coolant circuit for a combustion engine

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CH508831A (en) * 1969-05-29 1971-06-15 Sulzer Ag Machine with cooled stuffing box
CN2095951U (en) * 1990-12-07 1992-02-12 温岭县部渎前溪机械厂 Self-suction automatic water pump
DE19901123A1 (en) * 1999-01-14 2000-07-20 Bosch Gmbh Robert Controllable radial pump, especially for supplying coolant for car has adjuster connected with sleeve which can be slid over pump blades in axial direction
DE102008026218B4 (en) * 2008-05-30 2012-04-19 Geräte- und Pumpenbau GmbH Dr. Eugen Schmidt Adjustable coolant pump
DE102008049204A1 (en) * 2008-09-27 2010-04-01 Man Nutzfahrzeuge Ag Cooling system for vehicles with liquid-cooled internal combustion engine

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Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20120204818A1 (en) * 2011-02-15 2012-08-16 Schwabische Huttenwerke Automotive Gmbh Coolant pump which exhibits an adjustable delivery volume
EP2489881A3 (en) * 2011-02-15 2013-04-03 Schwäbische Hüttenwerke Automotive GmbH Coolant pump with adjustable capacity
US9080573B2 (en) 2011-02-15 2015-07-14 Schwäbische Hüttenwerke Automotive GmbH Coolant pump which exhibits an adjustable delivery volume
WO2017076645A1 (en) * 2015-11-06 2017-05-11 Pierburg Gmbh Coolant pump for an internal combustion engine
WO2017076524A1 (en) * 2015-11-06 2017-05-11 Pierburg Gmbh Coolant pump for the automotive industry
CN108350886A (en) * 2015-11-06 2018-07-31 皮尔伯格有限责任公司 Coolant pump for automotive field
US10508650B2 (en) 2015-11-06 2019-12-17 Pierburg Gmbh Coolant pump for an internal combustion engine
CN108350886B (en) * 2015-11-06 2020-03-03 皮尔伯格有限责任公司 Coolant pump for the automotive field
US10982676B2 (en) 2015-11-06 2021-04-20 Pierburg Gmbh Coolant pump for the automotive industry
EP3290713A1 (en) * 2016-09-06 2018-03-07 Pierburg GmbH Coolant pump for the automotive sector and a coolant circuit for a combustion engine

Also Published As

Publication number Publication date
CN102477996A (en) 2012-05-30
KR20120054537A (en) 2012-05-30
EP2455615A3 (en) 2014-04-09
CN102477996B (en) 2016-03-30
KR101819750B1 (en) 2018-01-17
EP2455615B1 (en) 2017-08-16

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