EP2169233B1 - Cooling system for vehicles with fluid-cooled combustion engine - Google Patents
Cooling system for vehicles with fluid-cooled combustion engine Download PDFInfo
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- EP2169233B1 EP2169233B1 EP09009316.2A EP09009316A EP2169233B1 EP 2169233 B1 EP2169233 B1 EP 2169233B1 EP 09009316 A EP09009316 A EP 09009316A EP 2169233 B1 EP2169233 B1 EP 2169233B1
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- pump
- cooling system
- coolant
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- 238000001816 cooling Methods 0.000 title claims description 45
- 238000002485 combustion reaction Methods 0.000 title claims description 27
- 239000002826 coolant Substances 0.000 claims description 39
- 230000001105 regulatory effect Effects 0.000 claims description 11
- 239000000470 constituent Substances 0.000 claims 1
- 238000005192 partition Methods 0.000 description 9
- 239000000110 cooling liquid Substances 0.000 description 8
- 230000006835 compression Effects 0.000 description 3
- 238000007906 compression Methods 0.000 description 3
- 238000011161 development Methods 0.000 description 2
- 230000018109 developmental process Effects 0.000 description 2
- 230000002349 favourable effect Effects 0.000 description 2
- 238000010438 heat treatment Methods 0.000 description 2
- 238000007726 management method Methods 0.000 description 2
- 230000002093 peripheral effect Effects 0.000 description 2
- 230000003213 activating effect Effects 0.000 description 1
- 230000006978 adaptation Effects 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 239000007788 liquid Substances 0.000 description 1
- 230000007257 malfunction Effects 0.000 description 1
- 238000003825 pressing Methods 0.000 description 1
- 238000005096 rolling process Methods 0.000 description 1
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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
- F04D15/00—Control, e.g. regulation, of pumps, pumping installations or systems
- F04D15/02—Stopping of pumps, or operating valves, on occurrence of unwanted conditions
- F04D15/0209—Stopping of pumps, or operating valves, on occurrence of unwanted conditions responsive to a condition of the working fluid
-
- 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
- F01P7/16—Controlling of coolant flow the coolant being liquid by thermostatic control
- F01P7/161—Controlling of coolant flow the coolant being liquid by thermostatic control by bypassing 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
- F04D1/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal 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
- F01P7/00—Controlling of coolant flow
- F01P7/14—Controlling of coolant flow the coolant being liquid
- F01P2007/146—Controlling of coolant flow the coolant being liquid using valves
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- 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
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Description
Die vorliegende Erfindung betrifft ein Kühlsystem für Fahrzeuge, insbesondere Nutz- oder Kraftfahrzeuge mit flüssigkeitsgekühlter Brennkraftmaschine, gemäß dem Oberbegriff des Patentanspruchs 1.The present invention relates to a cooling system for vehicles, in particular commercial or motor vehicles with a liquid-cooled internal combustion engine, according to the preamble of claim 1.
Eine derartiges Kühlsystem für Verbrennungsmotoren beschreibt z.B. die
Weiter zeigt die
Aufgabe der Erfindung ist es, ein Kühlsystem mit einer regelbaren Kühlmittelpumpe für Fahrzeuge mit flüssigkeitsgekühlter Brennkraftmaschine derart weiterzubilden, dass unter Bereitstellung günstiger Wirkungsgrade und vielseitiger Steuerungsmöglichkeiten dieses Kühlsystem bedarfsgerecht versorgt werden kann.The object of the invention is to develop a cooling system with a controllable coolant pump for vehicles with a liquid-cooled internal combustion engine in such a way that this cooling system can be supplied as required while providing favorable efficiencies and versatile control options.
Diese Aufgabe wird erfindungsgemäß mit den Merkmalen des Patentanspruches 1 gelöst. Vorteilhafte Weiterbildungen der Erfindung sind Gegenstand der Unteransprüche.This object is achieved according to the invention with the features of claim 1. Advantageous further developments of the invention are the subject of the subclaims.
Gemäß Anspruch 1 wird vorgeschlagen, dass die z. B. konkret als Zentrifugalpumpe ausgebildete Kühlmittelpumpe zur Versorgung unterschiedlicher, voneinander getrennter Kühlmittelkreise mehr-, insbesondere zweiflutig mit mehreren, insbesondere zwei, Pumpenfluten ausgebildet ist, wobei zumindest eine der Pumpenfluten über das bevorzugt als Ringschieber ausgebildete Regelelement hinsichtlich der Förderleistung veränderlich ist. Daraus resultiert neben der Möglichkeit einer konstruktiv optimierten Auslegung der Pumpenfluten vor allem auch eine bedarfsgerechte Steuerung wenigstens einer der Pumpenfluten, so dass eine weitreichende Anpassung der Pumpenleistung an gegebene Einbauverhältnisse und Kühlleistungsanforderungen von Fahrzeugen geschaffen wird. Erfindungsgemäß ist vorgesehen, dass das Regelelement zur Regulierung der veränderlichen Förderleistung wenigstens einer der Pumpenfluten mittels einer vorgegebenen Menge eines Kühlmittels aus einer anderen, abgetrennten, ersten Pumpenflut beaufschlagbar ist.According to claim 1 it is proposed that the z. B. specifically designed as a centrifugal pump coolant pump for supplying different, separate coolant circuits multi-flow, in particular double-flow with several, in particular two, pump flows, with at least one of the pump flows via the control element, which is preferably designed as a ring slide, can be changed with regard to the delivery rate. In addition to the possibility of a structurally optimized design of the pump flows, this also results in a need-based control of at least one of the pump flows, so that a far-reaching adaptation of the Pump capacity is created for given installation conditions and cooling capacity requirements of vehicles. According to the invention it is provided that the regulating element for regulating the variable delivery rate of at least one of the pump flows can be acted upon by means of a predetermined amount of a coolant from another, separated, first pump flow.
Bevorzugt können dazu auf der Antriebswelle der Kühlmittelpumpe z. B. zwei Flügelräder des Pumpenlaufrades vorgesehen sein, die funktionell über eine Tennwand im Pumpenraum voneinander getrennt sind, wobei z. B. das dem Pumpengehäuse unmittelbar benachbarte Flügelrad mit einem Ringschieber als Regelelement zusammenwirkt. Die Flügelräder sind bevorzugt durch ein in sich unterteiltes, einstückiges Flügelrad gebildet. Der Begriff Flügelrad ist hier zudem in einem weiteren Sinne zu verstehen und soll grundsätzlich jegliche geeignete Laufradgeometire umfassen.Preferably, on the drive shaft of the coolant pump z. B. two impellers of the pump impeller can be provided, which are functionally separated from each other by a partition wall in the pump room, z. B. the impeller immediately adjacent to the pump housing cooperates with a ring slide as a control element. The impellers are preferably formed by a subdivided, one-piece impeller. The term impeller is to be understood here in a broader sense and should in principle encompass any suitable impeller geometry.
Gemäß einer bevorzugten konkreten Ausführungsform mit zwei Pumpenfluten ist vorgesehen, mit einer ersten Pumpenflut das Kühlsystem der Brennkraftmaschine und mit einer in der Durchflussmenge veränderlichen, zweiten Pumpenflut einen Niedertemperatur-Kreislauf der Brennkraftmaschine zu versorgen. Dies ergibt eine baulich kompakte und kostengünstige Konstruktion eines Kühlsystems. Besonders bevorzugt kann dabei im konkreten Beispielfall die erste Pumpenflut auf eine höhere Fördermenge als die zweite Pumpenflut durch entsprechende Aufteilung der beiden zumindest funktionell getrennten Flügelräder ausgelegt sein. So kann z.B. der Hauptkühlkreislauf der Brennkraftmaschine auf bis zu 80% Pumpenleistung und der Nebenkühlkreislauf bzw. Niedertemperaturkühlkreislauf auf etwa 20% ausgelegt sein, wobei durch die bedarfsgerechte Steuerung ein weiterer konstruktiver Eingriff gegeben ist.According to a preferred specific embodiment with two pump flows, the cooling system of the internal combustion engine is supplied with a first pump flow and a low-temperature circuit of the internal combustion engine is supplied with a second pump flow variable in the flow rate. This results in a structurally compact and inexpensive construction of a cooling system. Particularly preferably, in the specific example, the first pump flow can be designed for a higher delivery rate than the second pump flow by appropriate division of the two at least functionally separate impellers. For example, the main cooling circuit of the internal combustion engine can be designed for up to 80% pump output and the secondary cooling circuit or low-temperature cooling circuit for around 20%, with the need-based control providing a further structural intervention.
Des Weiteren kann die hinsichtlich ihrer Förderleistung veränderliche Pumpenflut in ihrer konstruktiv festgelegten Fördermenge so ausgelegt sein, dass bei voller Förderleistung ein definierter Systemdruck im zugeordneten Kühlmittel nicht überschritten wird. Diese Auslegung und ggf. Steuerung der Durchsatzmenge der hinsichtlich der Förderleistung veränderlichen Pumpenflut ermöglicht es, ein im z. B. Niedertemperaturkreislauf als Nebenkühlkreislauf ansonsten eingesetztes Überdruckventil entfallen zu lassen.Furthermore, the pump flow, which is variable in terms of its delivery rate, can be designed in terms of its structurally determined delivery rate so that a defined system pressure in the associated coolant is not exceeded at full delivery rate. This design and, if necessary, control of the throughput of the variable pump flow in terms of delivery rate enables a z. B. to omit the low-temperature circuit as a secondary cooling circuit otherwise used overpressure valve.
Das Regelelement ist, wie bereits zuvor erwähnt, bevorzugt als Ringschieber ausgebildet. Dieser Ringschieber kann über z. B. Federn als Kraftspeicher in eine die volle Fördermenge der hinsichtlich der Förderleistung veränderlichen Pumpenflut freigebende Stellung vorgespannt sein und wird besonders bevorzugt durch Druckbeauschlagung mittels eines Kühlmittelstroms einer ersten Pumpenflut auf deren Druckseite betätigt. Damit ist eine besonders einfache Steuerung der zweiten Pumpenflut abhängig vom Druckverlauf auf der Druckseite der ersten Pumpenflut geschaffen, wobei auf zusätzliche Druckmittelquellen verzichtet werden kann.As mentioned above, the regulating element is preferably designed as an annular slide. This ring slide can be via z. B. springs as an energy store in a position releasing the full flow rate of the variable flow rate of the pump flow and is particularly preferably actuated by applying pressure by means of a coolant flow of a first pump flow on the pressure side. This creates a particularly simple control of the second pump flow depending on the pressure profile on the pressure side of the first pump flow, it being possible to dispense with additional pressure medium sources.
In vorteilhafter Weiterbildung dieses Erfindungsaspektes kann auch die erste Pumpenflut über ein zweites Verstellmittel in ihrer Fördermenge verstellbar ausgeführt sein. Dies stellt eine noch weitergehende, bedarfsgerechte Steuerung der z. B. Zentrifugalpumpe als Kühlmittelpumpe sicher, wodurch u.a. auch eine besonders schnelle Erwärmung der Brennkraftmaschine auf Betriebstemperatur und ein noch günstigerer Pumpenwirkungsgrad steuerbar ist.In an advantageous further development of this aspect of the invention, the delivery rate of the first pump flow can also be designed to be adjustable via a second adjusting means. This provides an even more extensive, needs-based control of the z. B. centrifugal pump as a coolant pump, which among other things, a particularly rapid heating of the internal combustion engine to operating temperature and an even more favorable pump efficiency can be controlled.
Dabei können in bevorzugter Weise die zweiten Verstellmittel ebenfalls durch einen Ringschieber gebildet sein, der temperatur-, drehzahl- und/oder druckabhängig über eine von der Brennkraftmaschine betriebene Druckmittelquelle beaufschlagt ist. Die Druckmittelquelle kann insbesondere eine von der Brennkraftmaschine ohnehin angetriebene Servoeinrichtung, z.B. eine hydraulische Servolenkung etc. sein. Auch eine Druckluftquelle kann eingesetzt werden. Schließlich kann dieser Ringschieber auch in einem mit dem Pumpengehäuse kommunizierenden, den Pumpenraum zumindest teilweise umgebenden Gehäuse angeordnet sein. Das Gehäuse kann dabei entweder ein separates, an die Brennkraftmaschine anschließendes Aufnahmegehäuse (Kühlmittelverteilergehäuse) sein, in das das Pumpengehäuse eingeschoben wird, und/oder das Zylindergehäuse der Brennkraftmaschine sein, an das die Zentrifugalpumpe angebaut ist.In this case, the second adjustment means can preferably also be formed by an annular slide which is temperature, speed and / or pressure dependent via a pressure medium source operated by the internal combustion engine is applied. The pressure medium source can in particular be a servo device that is driven by the internal combustion engine anyway, for example a hydraulic power steering, etc. A compressed air source can also be used. Finally, this ring slide can also be arranged in a housing that communicates with the pump housing and at least partially surrounds the pump chamber. The housing can either be a separate receiving housing (coolant distributor housing) adjoining the internal combustion engine, into which the pump housing is inserted, and / or the cylinder housing of the internal combustion engine to which the centrifugal pump is attached.
Ferner können zweckmäßigerweise beide Kühlkreise bzw. beide Pumpenfluten separat an einen oder zwei Vorratsbehälter des Kühlsystems angeschlossen sein, um die übliche Ausdehnung des Kühlmediums bei dessen Erwärmung entsprechend auszugleichen.Furthermore, both cooling circuits or both pump flows can expediently be connected separately to one or two storage tanks of the cooling system in order to compensate for the usual expansion of the cooling medium when it is heated.
Ein Ausführungsbeispiel der Erfindung ist im Folgenden näher erläutert.An exemplary embodiment of the invention is explained in more detail below.
Es zeigen:
- Fig. 1
- ein Blockschaltbild eines Kühlsystems für eine turboaufgeladene Brennkraftmaschine für Kraftfahrzeuge, mit einer zweiflutigen Zentrifugalpumpe zur Versorgung eines ersten Hauptkühlkreises und eines zweiten Niedertemperatur-Kühlkreises mit Kühlflüssigkeit, wobei die zweite Pumpenflut mittels eines integrierten Ringschiebers bedarfsgerecht gesteuert ist, und
- Fig. 2
- einen Längsschnitt durch die skizzenhaft dargestellte Zentrifugalpumpe gemäß
Fig. 1 , in der Offenstellung des Ringschiebers.
- Fig. 1
- a block diagram of a cooling system for a turbo-charged internal combustion engine for motor vehicles, with a double-flow centrifugal pump for supplying a first main cooling circuit and a second low-temperature cooling circuit with cooling liquid, the second pump flow being controlled as required by means of an integrated ring slide, and
- Fig. 2
- a longitudinal section through the sketched centrifugal pump according to
Fig. 1 , in the open position of the ring slide.
In der
Die Zentrifugalpumpe 4 wird über eine Antriebswelle 5 und ein Antriebsrad 6 über einen nicht dargestellten Riementrieb von der Brennkraftmaschine angetrieben.The
Die Zentrifugalpumpe 4 ist zweiflutig ausgebildet und versorgt druckseitig in einem ersten Hochtemperatur-Kühlkreislauf über eine nur angedeutete Druckleitung 7 die Brennkraftmaschine mit Kühlflüssigkeit, die über eine Rücklaufleitung 8 mit einem ersten luftdurchströmten Wärmetauscher 9a als Hochtemperatur-Wärmetauscher kommuniziert.The
Eine Ansaugleitung 10a leitet die rückgekühlte Kühlflüssigkeit zu einer Ansaugöffnung 11a der Zentrifugalpumpe 4. Der beschriebene erste Kühlkreislauf versorgt in bekannter Weise die gesamte Brennkraftmaschine, ferner z.B. ein nicht dargestelltes Heizsystem des Innenraums des Kraftfahrzeuges, etc.An
Der zweite Niedertemperatur-Kreislauf weist eine an die zweite Pumpenflut der Zentrifugalpumpe 4 angeschlossene Druckleitung 12 auf, die mit einem Ladeluftkühler 13 verbunden ist. Über eine Rücklaufleitung 14 strömt die Kühlflüssigkeit zu einem zweiten luftdurchströmten Wärmetauscher 9b als Niedertemperatur-Wärmetauscher, von wo aus die Kühlflüssigkeit dann über eine Rücklaufleitung 10b zu einer Ansaugöffnung 11b der Zentrifugalpumpe 4 zurückströmt. Der Ladeluftkühler 13 ist an nur angedeutete Ladeluftleitungen 15, 16 angeschlossen und dient zur Rückkühlung von verdichteter, der Brennkraftmaschine zugeführter Verbrennungsluft.The second low-temperature circuit has a
Beide Kühlkreisläufe sind über Leitungen 17a, 17b, die von den Rücklaufleitungen 8, 14 abzweigen, mit einem teilweise mit Kühlflüssigkeit befüllten Ausgleichsbehälter 18 verbunden.Both cooling circuits are connected via
Die
Die Antriebswelle 5 ist in dem Pumpengehäuse 19 mittels einer nicht näher dargestellten Wälzlagerung 22 drehbar gelagert und nach außen abgedichtet und trägt einerseits das Antriebsrad 6 und andererseits das Pumpenlaufrad 20, das in den Pumpenraum 3 eines Aufnahmegehäuses, z. B. in das Zylindergehäuse 1 der Brennkraftmaschine und/oder das Kühlmittelverteilergehäuse 1a einragt.The
Das Pumpenlaufrad 20 weist eine laufradseitige innere Trennwand 20a auf, die im Pumpenraum 3 mit einer ringförmigen Trennwand 23 zusammenwirkt und den Pumpenraum 3 in zwei Pumpenfluten 34, 35 unterteilt. Beide Pumpenfluten 34, 35 sind dadurch voneinander getrennt, wobei jedoch minimale Leckagen zugelassen sind. Die Trennwand 23 ist bevorzugt integraler Bestandteil des Pumpengehäuses 19 und unterteilt somit den Pumpenraum 3 so, dass druckseitig die beiden Abströmöffnungen 24, 25 zu den Druckleitungen 7, 12 voneinander getrennt sind.The
Jeder der beiden Pumpenfluten 34, 35 ist jeweils ein Flügelrad 20b, 20c des Pumpenlaufrades 20 zugeordnet bzw. im Wesentlichen durch diese gebildet, wobei sich, zwischen den Flügelrädern 20b, 20c die innere Trennwand 20a als Flügelrad-Abtrennelement erstreckt und die Flügelräder 20b und 20c voneinander funktionell trennt.Each of the two pump flows 34, 35 is assigned an
Die Zentrifugalpumpe 4 bzw. das Pumpenlaufrad 20 saugt über die Ansaugöffnung 11a Kühlflüssigkeit in die Pumpenflut 34 bzw. über die lediglich äußerst schematisch und beispielhaft eingezeichnete Ansaugöffnung 11b Kühlflüssigkeit in die Pumpenflut 35 an und fördert diese mittels der zwei Flügelräder 20b, 20c über die Abströmöffnungen 24, 25 radial nach außen zu den in der
An der Rückseite des Pumpenlaufrades 20 ist eine ringförmige Basisplatte 26 ausgebildet, die mehrere in Umfangsrichtung voneinander bevorzugt gleichmäßig beabstandete Führungsbolzen 27 (in der Schnittzeichnung
Zwischen der Radialwand 21a des Ringschiebers 21 und der Basisplatte 26 sind mehrere, z. B. drei umfangsmäßig verteilte Schraubendruckfedern 28 in einem bevorzugt gleichen Abstand vorgesehen, die den Ringschieber 21 in die in der
In dem Nabenabschnitt 19b des Pumpengehäuses 19 sind mehrere, z. B. drei umfangsmäßig verteilte und vorzugsweise einen gleichen Abstand voneinander aufweisende Stellkolben 29 verschiebbar gelagert, die über einen hier lediglich äußerst schematisch dargestellten wälzgelagerten Druckring 30 an der Radialwand 21a des Ringschiebers 21 anliegen.In the
Die Stellkolben 29 bzw. deren Lagerbohrungen münden in einen Ringraum 19c des Nabenabschnittes 19b und können über diesen mit Kühlmittel aus der ersten Pumpenflut 34 in noch näher zu beschreibender Weise druckbeaufschlagt werden, so dass der Ringschieber 21 in die die Fördermenge an Kühlflüssigkeit vermindernde Position ausgefahren wird. Dazu ist an den Ringraum 19c eine Druckleitung 31 angeschlossen, die über Stichkanäle 32, 33 im Zylindergehäuse 1 mit dem Pumpenraum 3 bzw. mit der ersten Pumpenflut 34 zur Versorgung des ersten Kühlkreises im Bereich der Abströmöffnung 24 strömungsverbunden ist. Dementsprechend kann sich gemäß dieser besonders vorteilhaften Ausgestaltung der Pumpendruck der ersten Pumpenflut 34 über die Druckleitung 31 in den Ringraum 19c fortpflanzen und bestimmt in steuerungstechnisch einfacher Weise die Fördermenge und den Förderdruck der zweiten Pumpenflut 35 in dem vorbeschriebenen Niedertemperatur-Kreislauf.The actuating
Die Schraubendruckfedern 28 stellen sicher, dass bei ggf. auftretenden Störungen die zweite Pumpenflut 35 des Flügelrades 20 voll funktionsfähig ist bzw. mit der konstruktiv vorgesehenen, maximalen Fördermenge arbeitet.The helical compression springs 28 ensure that, in the event of any malfunctions, the
Die Pumpenfluten 34, 35 mit der Trennwand 20a im Pumpenlaufrad 20 und der Trennwand 23 im Pumpenraum 3 sind konstruktiv z. B. so ausgelegt, dass in der
In nicht dargestellter Weise kann ggf. auch die erste Pumpenflut 34 über ein zweites Verstellmittel in ihrer Fördermenge verstellbar ausgeführt sein.In a manner not shown, the first pump flow 34 can optionally also be designed to be adjustable in terms of its delivery rate via a second adjusting means.
Die zweiten Verstellmittel können dabei ebenfalls durch einen Ringschieber gebildet sein, der temperatur- , drehzahl- und/oder druckabhängig über eine von der Brennkraftmaschine betriebene Druckmittelquelle z.B. hydraulisch oder pneumatisch beaufschlagt ist und der bevorzugt in einem mit dem Pumpengehäuse bzw. dem Zylindergehäuse 1 und/oder Kühlmittelverteilergehäuse 1a kommunizierenden, den Pumpenraum 3 zumindest teilweise umgebenden Gehäuse angeordnet ist.The second adjustment means can also be formed by a ring slide, which is acted upon by a pressure medium source operated by the internal combustion engine, e.g. hydraulically or pneumatically, depending on temperature, speed and / or pressure and which is preferably in a with the pump housing or the cylinder housing 1 and / or the
Das Pumpenlaufrad 20 kann ggf. durch zwei axial benachbart zueinander angeordnete Flügelräder gebildet sein, die ggf. mit unterschiedlichen Außendurchmessern und/oder Breiten ausgeführt sind, um deren Förderleistungen und damit die Pumpenfluten entsprechend auszulegen.The
- 11
- ZylindergehäuseCylinder housing
- 1a1a
- KühlmittelverteilergehäuseCoolant distributor housing
- 22
- StirnseiteFront side
- 33
- PumpenraumPump room
- 44th
- Zentrifugalpumpecentrifugal pump
- 55
- Antriebswelledrive shaft
- 66th
- Antriebsraddrive wheel
- 77th
- DruckleitungPressure line
- 88th
- RücklaufleitungReturn line
- 9a9a
- Hochtemperatur-WärmetauscherHigh temperature heat exchanger
- 10a10a
- Rücklaufleitung vom Hochtemperatur-WärmetauscherReturn line from the high temperature heat exchanger
- 10b10b
- Rücklaufleitung vom Niedertemperatur-WärmetauscherReturn line from the low temperature heat exchanger
- 11a11a
- Ansaugöffnung Hochtemperatur-KreislaufSuction opening high temperature circuit
- 11b11b
- Ansaugöffnung Niedertemperatur-KreislaufSuction opening low-temperature circuit
- 1212th
- DruckleitungPressure line
- 1313th
- LadeluftkühlerIntercooler
- 1414th
- RücklaufleitungReturn line
- 1515th
- LadeluftleitungCharge air line
- 1616
- LadeluftleitungCharge air line
- 17a17a
- Leitungmanagement
- 17b17b
- Leitungmanagement
- 1818th
- Ausgleichsbehältersurge tank
- 1919th
- Gehäusecasing
- 19a19a
- BefestigungsflanschMounting flange
- 19b19b
- NabenabschnittHub section
- 19c19c
- RingraumAnnulus
- 2020th
- PumpenlaufradPump impeller
- 20a20a
- Trennwandpartition wall
- 20b20b
- FlügelradImpeller
- 20c20c
- FlügelradImpeller
- 2121
- RingschieberRing slide
- 21a21a
- RadialwandRadial wall
- 21b21b
- UmfangswandPerimeter wall
- 2222nd
- WälzlagerungRolling bearings
- 2323
- Trennwandpartition wall
- 2424
- AbströmöffnungDischarge opening
- 2525th
- AbströmöffnungDischarge opening
- 2626th
- RückwandBack wall
- 2727
- Bolzenbolt
- 2828
- SchraubendruckfedernHelical compression springs
- 2929
- StellkolbenControl piston
- 3030th
- DruckringPressure ring
- 3131
- DruckleitungPressure line
- 3232
- StichkanalBranch channel
- 3333
- StichkanalBranch channel
- 3434
- erste Pumpenflutfirst pump flood
- 3535
- zweite Pumpenflutsecond flood of pumps
Claims (12)
- Cooling system for liquid-cooled internal combustion engines, having a regulable coolant pump (4) and having a regulating element (21) which regulates the throughflow rate, wherein the coolant pump (4) is of multichannel design with multiple pump channels (34, 35), which are assigned to coolant circuits which are in each case separated from one another, wherein at least one of the pump channels (35) is, by means of the regulating element (21), variable in terms of its delivery power, characterized in that, for regulating the variable delivery power of at least one of the pump channels (35), the regulating element (21) is able to be charged by means of a predefined quantity of a coolant from another, separated, first pump channel (34).
- Cooling system according to Claim 1, characterized in that, in terms of their delivery power, the pump channels (34, 35) are of different design, and regulation of the delivery power of at least one of the pump channels (34, 35) is realized by means of the regulating element (21) within predefined setting ranges.
- Cooling system according to Claim 2, characterized in that a first pump channel (34) provides a supply to a cooling system of the internal combustion engine, and a second pump channel (35), which is variable in terms of throughflow rate, provides a supply to a low-temperature circuit of the internal combustion engine, wherein the first pump channel (34) is designed for a higher delivery pressure than the second pump channel (35), in particular as a result of corresponding division and/or design of impellers (20b, 20c) which are assigned to the pump channels (34, 35) and are at least functionally separate.
- Cooling system according to one of Claims 1 to 3, characterized in that the two pump channels (34, 35) are connected in terms of flow by means of at least one flow transfer line (31), wherein the flow transfer line (31) is preferably in the form of a pressure line branching off from the pressure side of the first pump channel (34), which first pump channel pumps over the coolant.
- Cooling system according to Claim 4, characterized in that the flow transfer line (31) opens into a pressure space (19c) assigned to the regulating element (21) such that the regulating element (21) is displaceable along its predefined adjustment path according to the coolant quantity delivered into the pressure space (19c), and thus completely opens up or at least partially closes off the respective pump channel (35), which is variable in terms of the delivery power.
- Cooling system according to Claim 5, characterized in that the flow transfer line (31) opens into a pressure space (19c), in the form of an annular space around a drive shaft (5) of the pump, between the pump housing (19) and the regulating element (21), which is in the form of an annular slide.
- Cooling system according to one of Claims 1 to 6, characterized in that the at least one pump channel (35) which is variable in terms of its delivery power is, in terms of its delivery power, designed in such a way that, at full delivery power, a defined pump pressure is not exceeded in the assigned coolant circuit.
- Cooling system according to one of Claims 1 to 7, characterized in that the pump channels (34, 35), in the pump space (3), are separated, by means of a dividing wall (23) forming preferably an integral constituent part of a pump housing (19), completely from one another or, with provision of leaks of a defined order of magnitude, substantially from one another.
- Cooling system according to one of Claims 1 to 8, characterized in that the pump channels (34, 35) are each assigned a separate impeller (20b, 20c) of a pump rotor (20).
- Cooling system according to Claim 9, characterized in that the impellers (20b, 20c) are arranged on a common drive shaft (5) of the coolant pump and are driven by said shaft.
- Cooling system according to one of Claims 1 to 10, characterized in that the different coolant circuits or pump channels (34, 35) are connected to a compensation tank (18).
- Cooling system according to one of Claims 1 to 11, characterized in that the two pump channels (34, 35) are each designed to be adjustable in terms of their delivery rate via an adjustment means.
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102008049204A DE102008049204A1 (en) | 2008-09-27 | 2008-09-27 | Cooling system for vehicles with liquid-cooled internal combustion engine |
Publications (3)
Publication Number | Publication Date |
---|---|
EP2169233A2 EP2169233A2 (en) | 2010-03-31 |
EP2169233A3 EP2169233A3 (en) | 2017-03-29 |
EP2169233B1 true EP2169233B1 (en) | 2021-03-31 |
Family
ID=41259147
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP09009316.2A Active EP2169233B1 (en) | 2008-09-27 | 2009-07-17 | Cooling system for vehicles with fluid-cooled combustion engine |
Country Status (2)
Country | Link |
---|---|
EP (1) | EP2169233B1 (en) |
DE (1) | DE102008049204A1 (en) |
Families Citing this family (16)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102010025560B4 (en) | 2010-06-30 | 2019-03-07 | Iav Gmbh Ingenieurgesellschaft Auto Und Verkehr | Switchable coolant pump |
DE102010026132A1 (en) * | 2010-07-05 | 2012-01-05 | Mahle International Gmbh | Rotor for liquid pump for cooling circuit of internal combustion engine, has pressure relief valve integrated into rotor and forming path depending on difference between pressure side and suction side, where back path opens pressure side |
DE102010046316B4 (en) * | 2010-09-23 | 2020-03-19 | Audi Ag | Pump drive with viscous coupling and mechanical speed control |
EP2455615B1 (en) * | 2010-11-19 | 2017-08-16 | MAHLE International GmbH | Pump |
DE102010044167A1 (en) * | 2010-11-19 | 2012-05-24 | Mahle International Gmbh | 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 |
DE102011012826B3 (en) * | 2011-03-02 | 2012-01-12 | Geräte- und Pumpenbau GmbH Dr. Eugen Schmidt | Controllable coolant pump for internal combustion engine of motor car, has passage hole arranged between pressure channel and pressure chamber before magnetic valve, where magnetic valve produces defined pressurization of regulating valve |
DE102011001090A1 (en) * | 2011-03-04 | 2012-09-06 | Geräte- und Pumpenbau GmbH Dr. Eugen Schmidt Merbelsrod | Controllable cooling system for a motor vehicle, coolant pump therefor, usable in the coolant pump impeller and method for controlling a flow of coolant in such a cooling system |
DE102011079311A1 (en) * | 2011-07-18 | 2013-01-24 | Schaeffler Technologies AG & Co. KG | Coolant pump for coolant circulation circuit of internal combustion engine of motor car, has control pump integrated into pump and providing fluid for displacement of locking element, where control pump is designed as rotary pump |
DE102011113040B3 (en) * | 2011-09-09 | 2012-04-26 | Geräte- und Pumpenbau GmbH Dr. Eugen Schmidt | Controllable coolant pump for supplying coolant to e.g. cylinder head of internal combustion engine, has outflow opening enclosed by ring seal, which is arranged in chamber rear wall and actively connected with disk in rear end position |
DE102012214503B4 (en) | 2012-08-14 | 2017-10-12 | Schwäbische Hüttenwerke Automotive GmbH | Rotary pump with adjustable delivery volume, in particular for adjusting a coolant pump |
US9739194B2 (en) | 2013-03-04 | 2017-08-22 | Ford Global Technologies, Llc | Charge-air intercooler system with integrated heating device |
DE102014219565B4 (en) * | 2013-10-07 | 2015-10-15 | Schaeffler Technologies AG & Co. KG | Outer actuator for a runner cover of an adjustable water pump |
DE102014202979A1 (en) * | 2014-02-18 | 2015-08-20 | Volkswagen Aktiengesellschaft | pump |
DE102014004009A1 (en) * | 2014-03-20 | 2015-12-03 | Daimler Ag | Coolant circuit for cooling an internal combustion engine, in particular for a motor vehicle, and method for operating such a coolant circuit |
DE102014009367B3 (en) | 2014-06-21 | 2015-03-05 | Geräte- und Pumpenbau GmbH Dr. Eugen Schmidt | Adjustable coolant pump |
DE102016116636B4 (en) * | 2016-09-06 | 2019-08-14 | Pierburg Gmbh | Coolant pump for the automotive sector and a coolant circuit for an internal combustion engine |
Family Cites Families (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102005062200B3 (en) | 2005-12-23 | 2007-02-22 | Geräte- und Pumpenbau GmbH Dr. Eugen Schmidt | Adjustable coolant pump for internal combustion engine has annular valve pusher fitted to several piston rods movable in pump housing |
DE102006034960B4 (en) * | 2006-07-28 | 2008-05-15 | Audi Ag | Coolant pump for a cooling circuit of an internal combustion engine |
-
2008
- 2008-09-27 DE DE102008049204A patent/DE102008049204A1/en not_active Ceased
-
2009
- 2009-07-17 EP EP09009316.2A patent/EP2169233B1/en active Active
Non-Patent Citations (1)
Title |
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None * |
Also Published As
Publication number | Publication date |
---|---|
EP2169233A3 (en) | 2017-03-29 |
DE102008049204A1 (en) | 2010-04-01 |
EP2169233A2 (en) | 2010-03-31 |
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