EP2169233A2 - Cooling system for vehicles with fluid-cooled combustion engine - Google Patents

Cooling system for vehicles with fluid-cooled combustion engine Download PDF

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Publication number
EP2169233A2
EP2169233A2 EP09009316A EP09009316A EP2169233A2 EP 2169233 A2 EP2169233 A2 EP 2169233A2 EP 09009316 A EP09009316 A EP 09009316A EP 09009316 A EP09009316 A EP 09009316A EP 2169233 A2 EP2169233 A2 EP 2169233A2
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EP
European Patent Office
Prior art keywords
pump
cooling system
pumping
coolant
flow
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
EP09009316A
Other languages
German (de)
French (fr)
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EP2169233B1 (en
EP2169233A3 (en
Inventor
Norbert Schatz
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.)
MAN Truck and Bus SE
Original Assignee
MAN Nutzfahrzeuge AG
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Publication date
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Publication of EP2169233A2 publication Critical patent/EP2169233A2/en
Publication of EP2169233A3 publication Critical patent/EP2169233A3/en
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • 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
    • 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 cooling system for vehicles, in particular commercial or motor vehicles with liquid-cooled internal combustion engine, according to the preamble of patent claim 1.
  • Such a cooling system for internal combustion engines describes the example DE 10 2005 062 200 B3 , in which the cooling circuit of the liquid cooling is supplied via a single-flow centrifugal pump, the flow rate of which is variable by means of the impeller more or less covering annular slide.
  • the annular slide is pneumatically acted upon by a separate pressure medium source and serves for a demand-based control of the flow rate or pump power within a coolant circuit.
  • the object of the invention is to develop a cooling system with a controllable coolant pump for vehicles with liquid-cooled internal combustion engine such that, while providing favorable efficiencies and versatile control options this cooling system can be supplied as needed.
  • the z. B. specifically designed as a centrifugal pump coolant pump to supply different, separate coolant circuits Pl-, in particular two-flow with several, especially two, pumping is formed and at least one of the pumping flows via the preferably designed as an annular slide control element in terms of flow rate is variable.
  • impellers of the pump impeller which are functionally separated from each other via a partition wall in the pump room, wherein z. B. the pump housing immediately adjacent impeller cooperates with an annular slide as a control element.
  • the impellers are preferably formed by a self-dividing, one-piece impeller.
  • impeller is also to be understood in a broader sense and should in principle include any suitable Laufradgeometire.
  • the first pump flood can be designed for a higher delivery rate than the second pump flood by corresponding division of the two at least functionally separated impellers.
  • the main cooling circuit of the internal combustion engine to up to 80% pump capacity and the secondary cooling circuit or low-temperature cooling circuit can be designed to about 20%, which is given by the needs-based control further constructive intervention.
  • variable in terms of their delivery rate pump flow can be designed in their constructive flow rate so that at full capacity a defined system pressure in the associated coolant is not exceeded.
  • This interpretation and possibly control of the flow rate of variable with respect to the flow rate pump flood makes it possible in z.
  • B. low temperature circuit can be omitted as a secondary cooling circuit otherwise used pressure relief valve.
  • the control element is, as already mentioned, preferably designed as a slide ring.
  • This slide ring can over z.
  • Druckbeauschlagung means of a coolant flow of a first pump surge on the pressure side.
  • the first pump surge can also be made adjustable in its flow rate via a second adjusting means.
  • This provides an even more advanced, needs-based control of z. B. centrifugal pump as a coolant pump safely, thereby including a particularly rapid heating of the internal combustion engine to operating temperature and even more favorable pump efficiency is controllable.
  • the second adjustment means may also be formed by an annular slide, which is subjected to temperature, speed and / or pressure-dependent via a pressure medium source operated by the internal combustion engine.
  • the pressure medium source may, in particular, comprise a servo device, which is in any case driven by the internal combustion engine, e.g. be a hydraulic power steering etc.
  • a compressed air source can also be used.
  • this annular slide can also be arranged in a communicating with the pump housing, the pump chamber at least partially surrounding housing.
  • the housing can be either a separate, subsequent to the internal combustion engine receiving housing (coolant distributor housing), in which the pump housing is inserted, and / or be the cylinder housing of the internal combustion engine, to which the centrifugal pump is attached.
  • both cooling circuits or both pump flows may expediently be connected separately to one or two reservoirs of the cooling system in order to compensate for the usual expansion of the cooling medium when it is heated.
  • a cylinder housing 1 of a multi-cylinder, liquid-cooled internal combustion engine is partially apparent, in whose end face 2 a pump chamber 3 is formed, in which a centrifugal pump 4 is used as an adjustable coolant pump by way of example.
  • a separate receiving housing can be provided as a coolant distributor housing 1 a, in which the centrifugal pump 4 is partially or completely inserted.
  • This coolant distributor housing 1 a is shown here only very schematically and dashed lines.
  • the centrifugal pump 4 is driven via a drive shaft 5 and a drive wheel 6 via a belt drive, not shown, of the internal combustion engine.
  • the centrifugal pump 4 is designed to be double-flowed and supplies the internal combustion engine with coolant, which communicates via a return line 8 with a first air-flowed heat exchanger 9a as a high-temperature heat exchanger in a first high-temperature cooling circuit via a pressure line 7 only indicated.
  • a suction line 10a leads the recooled cooling liquid to an intake opening 11a of the centrifugal pump 4.
  • the described first cooling circuit supplies the entire internal combustion engine in a known manner, Furthermore, for example, a not shown heating system of the interior of the motor vehicle, etc.
  • the second low-temperature circuit has a connected to the second pump surge of the centrifugal pump 4 pressure line 12 which is connected to a charge air cooler 13. Via a return line 14, the cooling liquid flows to a second air-flowed heat exchanger 9b as a low-temperature heat exchanger, from where the cooling liquid then flows back via a return line 10b to a suction port 11b of the centrifugal pump 4.
  • the intercooler 13 is connected to only indicated charge air lines 15, 16 and used for re-cooling of compressed, the internal combustion engine supplied combustion air.
  • Both cooling circuits are connected via lines 17a, 17b, which branch off from the return lines 8, 14, with a partially filled with coolant reservoir tank 18.
  • the Fig. 2 shows the centrifugal pump 4 in detail, which consists essentially of a pump housing 19, the drive shaft 5, the drive wheel 6, a double-flow pump impeller 20 and an axially adjustable annular slide 21.
  • the centrifugal pump 4 is not described so far known type.
  • the drive shaft 5 is rotatably supported in the pump housing 19 by means of a roller bearing 22, not shown in detail and sealed to the outside and carries on the one hand the drive wheel 6 and on the other hand, the pump impeller 20, in the pump chamber 3 of a receiving housing, for. B. in the cylinder housing 1 of the internal combustion engine and / or the coolant distributor housing 1 a protrudes.
  • the pump impeller 20 has an impeller-side inner partition wall 20a, which cooperates in the pump chamber 3 with an annular partition wall 23 and the pump chamber 3 in two pump flows 34, 35 divided. Both pump flows 34, 35 are separated from each other, but minimal leakage is allowed.
  • the partition wall 23 is preferably an integral part of the pump housing 19 and thus divides the pump chamber 3 so that the pressure side, the two outflow openings 24, 25 to the pressure lines 7, 12 are separated from each other.
  • Each of the two pumping passages 34, 35 is respectively associated with or substantially formed by an impeller 20b, 20c of the pump impeller 20, wherein between the impellers 20b, 20c the inner dividing wall 20a extends as an impeller separating element and the impellers 20b and 20c separates functionally from each other.
  • the centrifugal pump 4 and the pump impeller 20 sucks via the suction port 11 a cooling liquid into the pump flood 34 or via the only extremely schematic and exemplified suction port 11 b cooling liquid in the pump flow 35 and promotes these by means of the two impellers 20 b, 20 c on the Outflow openings 24, 25 radially outward to those in the Fig. 1 shown pressure lines 7, 12 of the first and second cooling circuit.
  • annular base plate 26 At the rear of the pump impeller 20, an annular base plate 26 is formed, which a plurality of circumferentially preferably uniformly spaced guide pin 27 (in the sectional drawing Fig. 2 only one guide pin 27 is visible) receives.
  • the guide pins 27 carry or guide a radial wall 21a of the annular slide 21, the peripheral wall 21 b covers the impeller 20b of the pump impeller 20 depending on the ring slide position to a predetermined extent and thus controls the flow rate of cooling liquid in the low-temperature cooling circuit.
  • annular slide 21 Between the radial wall 21 a of the annular slide 21 and the base plate 26 are more, z. B. three circumferentially distributed helical compression springs 28 provided in a preferably same distance, the annular slide 21 in the in the Fig. 2 shown biased retracted position in which the second pump surge 35 emits the full flow rate.
  • the adjusting pistons 29 or their bearing bores open into an annular space 19c of the hub portion 19b and can be pressurized via this with coolant from the first pumping flow 34 in a manner to be described further, so that the annular slide 21 is extended into the position reducing the delivery of cooling liquid ,
  • a pressure line 31 is connected to the annular space 19c, which is fluidly connected via branch channels 32, 33 in the cylinder housing 1 with the pump chamber 3 and with the first pumping flow 34 for supplying the first cooling circuit in the region of the outflow opening 24.
  • the pump pressure of the first pump flood 34 via the pressure line 31 in the annular space 19c propagate and determined in a simple control manner, the flow rate and the delivery pressure of the second pump surge 35 in the above-described low-temperature circuit.
  • the helical compression springs 28 ensure that if any faults occur, the second pump surge 35 of the impeller 20 is fully functional or works with the maximum design flow provided.
  • the pumping floods 34, 35 with the partition wall 20 a in the pump impeller 20 and the partition wall 23 in the pump chamber 3 are structurally z. B. designed so that in the Fig. 2 shown open position of the annular slide 21 z. B. about 80% of the flow rate of cooling fluid in the first main cooling circuit through the engine and about 20% in the second low-temperature cooling circuit with the intercooler 13 flow.
  • the open position is structurally z. B. designed so that in the Fig. 2 shown open position of the annular slide 21 z. B. about 80% of the flow rate of cooling fluid in the first main cooling circuit through the engine and about 20% in the second low-temperature cooling circuit with the intercooler 13 flow.
  • other presets are possible for the open position.
  • the flow rate and the delivery pressure of the low-temperature refrigeration circuit can be reduced by controlling the annular slide 21 via the delivery pressure of the first cooling circuit and the adjusting piston 29, the annular slide 21 with its peripheral wall 21 b, the impeller 20 c and accordingly the second pump flood 35 in enclose or cover given dimensions.
  • the first pumping flow 34 can also be designed so as to be adjustable in its flow rate via a second adjusting means.
  • the second adjusting means may also be formed by an annular slide, the temperature, speed and / or pressure-dependent via a driven by the internal combustion engine pressure medium source, for. is applied hydraulically or pneumatically and is preferably arranged in a communicating with the pump housing or the cylinder housing 1 and / or coolant distributor housing 1 a, the pump chamber 3 at least partially surrounding housing.
  • the impeller 20 may optionally be formed by two axially adjacent to each other arranged impellers, which are optionally designed with different outer diameters and / or widths to interpret their flow rates and thus the pump floods accordingly.

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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)

Abstract

The liquid-cooling system has coolant pump (4), where the flow in coolant pump is regulated by a control element. The coolant pump is formed with multiple two-pass, where each two-pass is separated by refrigerant circuits that are associated pump venting (35).

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 liquid-cooled internal combustion engine, according to the preamble of patent claim 1.

Eine derartiges Kühlsystem für Verbrennungsmotoren beschreibt z.B. die DE 10 2005 062 200 B3 , bei der der Kühlkreislauf der Flüssigkeitskühlung über eine einflutige Zentrifugalpumpe versorgt wird, deren Fördermenge mittels eines das Flügelrad mehr oder minder abdeckenden Ringschiebers veränderbar ist. Der Ringschieber wird pneumatisch über eine separate Druckmittelquelle beaufschlagt und dient zu einer bedarfsgerechten Steuerung der Durchflussmenge bzw. Pumpenleistung innerhalb eines Kühlmittelkreises.Such a cooling system for internal combustion engines describes the example DE 10 2005 062 200 B3 , in which the cooling circuit of the liquid cooling is supplied via a single-flow centrifugal pump, the flow rate of which is variable by means of the impeller more or less covering annular slide. The annular slide is pneumatically acted upon by a separate pressure medium source and serves for a demand-based control of the flow rate or pump power within a coolant circuit.

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 liquid-cooled internal combustion engine such that, while providing favorable efficiencies and versatile control options this cooling system can be supplied as needed.

Diese Aufgabe wird erfindungsgemäß mit den Merkmalen des Patentanspruches 1 gelöst. Vorteilhafte Weiterbildungen der Erfindung sind Gegenstand der Unteransprüche.This object is achieved by the features of claim 1. Advantageous developments of the invention are the subject of the dependent claims.

Erfindungsgemäß 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 und 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.According to the invention it is proposed that the z. B. specifically designed as a centrifugal pump coolant pump to supply different, separate coolant circuits mehr-, in particular two-flow with several, especially two, pumping is formed and at least one of the pumping flows via the preferably designed as an annular slide control element in terms of flow rate is variable. This results in addition to the possibility of structurally optimized design of the pump floods above all a need-based control of at least one of the pump floods, so that a far-reaching adjustment of the pump power to given installation conditions and cooling power requirements of vehicles is created.

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. be provided two impellers of the pump impeller, which are functionally separated from each other via a partition wall in the pump room, wherein z. B. the pump housing immediately adjacent impeller cooperates with an annular slide as a control element. The impellers are preferably formed by a self-dividing, one-piece impeller. The term impeller is also to be understood in a broader sense and should in principle include any suitable Laufradgeometire.

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 is provided to supply a low-temperature circuit of the internal combustion engine with a first pump flood the cooling system of the internal combustion engine and with a variable in the flow rate, second pump flow. This results in a structurally compact and cost-effective Construction of a cooling system. Particularly preferably, in the concrete example case, the first pump flood can be designed for a higher delivery rate than the second pump flood by corresponding division of the two at least functionally separated impellers. Thus, for example, the main cooling circuit of the internal combustion engine to up to 80% pump capacity and the secondary cooling circuit or low-temperature cooling circuit can be designed to about 20%, which is given by the needs-based control further constructive 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 variable in terms of their delivery rate pump flow can be designed in their constructive flow rate so that at full capacity a defined system pressure in the associated coolant is not exceeded. This interpretation and possibly control of the flow rate of variable with respect to the flow rate pump flood makes it possible in z. B. low temperature circuit can be omitted as a secondary cooling circuit otherwise used pressure relief 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.The control element is, as already mentioned, preferably designed as a slide ring. This slide ring can over z. B. springs biased as energy storage in a full delivery of the variable with respect to the delivery variable pumping position releasing position and is particularly preferably actuated by Druckbeauschlagung means of a coolant flow of a first pump surge on the pressure side. For a particularly simple control of the second pumping flood is created depending on the pressure curve on the pressure side of the first pump surge, which can be dispensed 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 development of this aspect of the invention, the first pump surge can also be made adjustable in its flow rate via a second adjusting means. This provides an even more advanced, needs-based control of z. B. centrifugal pump as a coolant pump safely, thereby including a particularly rapid heating of the internal combustion engine to operating temperature and even more favorable pump efficiency is controllable.

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, in a preferred manner, the second adjustment means may also be formed by an annular slide, which is subjected to temperature, speed and / or pressure-dependent via a pressure medium source operated by the internal combustion engine. The pressure medium source may, in particular, comprise a servo device, which is in any case driven by the internal combustion engine, e.g. be a hydraulic power steering etc. A compressed air source can also be used. Finally, this annular slide can also be arranged in a communicating with the pump housing, the pump chamber at least partially surrounding housing. The housing can be either a separate, subsequent to the internal combustion engine receiving housing (coolant distributor housing), in which the pump housing is inserted, and / or be 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 may expediently be connected separately to one or two reservoirs 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 embodiment of the invention is explained in more detail below.

Es zeigen:Show it:

Fig. 1Fig. 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, unda 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, wherein the second pump surge is controlled as required by means of an integrated annular slide, and
Fig. 2Fig. 2
einen Längsschnitt durch die skizzenhaft dargestellte Zentrifugalpumpe gemäß Fig. 1, in der Offenstellung des Ringschiebers.a longitudinal section through the sketched centrifugal pump according to Fig. 1 , in the open position of the ring valve.

In der Fig. 1 ist hier lediglich beispielhaft und schematisch ein Zylindergehäuse 1 einer mehrzylindrischen, flüssigkeitsgekühlten Brennkraftmaschine teilweise ersichtlich, in dessen Stirnseite 2 ein Pumpenraum 3 eingeformt ist, in den hier beispielhaft eine Zentrifugalpumpe 4 als regelbare Kühlmittelpumpe eingesetzt ist. Ebenso kann alternativ oder zusätzlich ein separates Aufnahmegehäuse als Kühlmittelverteilergehäuse 1 a vorgesehen sein, in das die Zentrifugalpumpe 4 zum Teil oder ganz eingesetzt ist. Dieses Kühlmittelverteilergehäuse 1 a ist hier lediglich äußerst schematisch und strichliert dargestellt.In the Fig. 1 Here, by way of example only and schematically, a cylinder housing 1 of a multi-cylinder, liquid-cooled internal combustion engine is partially apparent, in whose end face 2 a pump chamber 3 is formed, in which a centrifugal pump 4 is used as an adjustable coolant pump by way of example. Likewise, alternatively or additionally, a separate receiving housing can be provided as a coolant distributor housing 1 a, in which the centrifugal pump 4 is partially or completely inserted. This coolant distributor housing 1 a is shown here only very schematically and dashed lines.

Die Zentrifugalpumpe 4 wird über eine Antriebswelle 5 und ein Antriebsrad 6 über einen nicht dargestellten Riementrieb von der Brennkraftmaschine angetrieben.The centrifugal pump 4 is driven via a drive shaft 5 and a drive wheel 6 via a belt drive, not shown, of the internal combustion engine.

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 centrifugal pump 4 is designed to be double-flowed and supplies the internal combustion engine with coolant, which communicates via a return line 8 with a first air-flowed heat exchanger 9a as a high-temperature heat exchanger in a first high-temperature cooling circuit via a pressure line 7 only indicated.

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.A suction line 10a leads the recooled cooling liquid to an intake opening 11a of the centrifugal pump 4. The described first cooling circuit supplies the entire internal combustion engine in a known manner, Furthermore, for example, a not shown heating system of the interior of the motor vehicle, etc.

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 11 b 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 connected to the second pump surge of the centrifugal pump 4 pressure line 12 which is connected to a charge air cooler 13. Via a return line 14, the cooling liquid flows to a second air-flowed heat exchanger 9b as a low-temperature heat exchanger, from where the cooling liquid then flows back via a return line 10b to a suction port 11b of the centrifugal pump 4. The intercooler 13 is connected to only indicated charge air lines 15, 16 and used for re-cooling of compressed, the internal combustion engine supplied combustion air.

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 lines 17a, 17b, which branch off from the return lines 8, 14, with a partially filled with coolant reservoir tank 18.

Die Fig. 2 zeigt die Zentrifugalpumpe 4 im Detail, die sich im wesentlichen aus einem Pumpengehäuse 19, der Antriebswelle 5, dem Antriebsrad 6, einem zweiflutigen Pumpenlaufrad 20 und einem axial verstellbaren Ringschieber 21 zusammensetzt. Die Zentrifugalpumpe 4 ist soweit nicht beschrieben bekannter Bauart.The Fig. 2 shows the centrifugal pump 4 in detail, which consists essentially of a pump housing 19, the drive shaft 5, the drive wheel 6, a double-flow pump impeller 20 and an axially adjustable annular slide 21. The centrifugal pump 4 is not described so far known type.

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 1 a einragt.The drive shaft 5 is rotatably supported in the pump housing 19 by means of a roller bearing 22, not shown in detail and sealed to the outside and carries on the one hand the drive wheel 6 and on the other hand, the pump impeller 20, in the pump chamber 3 of a receiving housing, for. B. in the cylinder housing 1 of the internal combustion engine and / or the coolant distributor housing 1 a protrudes.

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 pump impeller 20 has an impeller-side inner partition wall 20a, which cooperates in the pump chamber 3 with an annular partition wall 23 and the pump chamber 3 in two pump flows 34, 35 divided. Both pump flows 34, 35 are separated from each other, but minimal leakage is allowed. The partition wall 23 is preferably an integral part of the pump housing 19 and thus divides the pump chamber 3 so that the pressure side, the two outflow openings 24, 25 to the pressure lines 7, 12 are separated from each other.

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 pumping passages 34, 35 is respectively associated with or substantially formed by an impeller 20b, 20c of the pump impeller 20, wherein between the impellers 20b, 20c the inner dividing wall 20a extends as an impeller separating element and the impellers 20b and 20c separates functionally from each other.

Die Zentrifugalpumpe 4 bzw. das Pumpenlaufrad 20 saugt über die Ansaugöffnung 11 a Kühlflüssigkeit in die Pumpenflut 34 bzw. über die lediglich äußerst schematisch und beispielhaft eingezeichnete Ansaugöffnung 11 b 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 Fig. 1 gezeigten Druckleitungen 7, 12 des ersten und zweiten Kühlkreises.The centrifugal pump 4 and the pump impeller 20 sucks via the suction port 11 a cooling liquid into the pump flood 34 or via the only extremely schematic and exemplified suction port 11 b cooling liquid in the pump flow 35 and promotes these by means of the two impellers 20 b, 20 c on the Outflow openings 24, 25 radially outward to those in the Fig. 1 shown pressure lines 7, 12 of the first and second cooling circuit.

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 Fig. 2 ist nur ein Führungsbolzen 27 ersichtlich) aufnimmt. Die Führungsbolzen 27 tragen bzw. führen eine Radialwand 21a des Ringschiebers 21, dessen Umfangswand 21 b das Flügelrad 20b des Pumpenlaufrades 20 je nach Ringschieber-Stellung in einem vorgegebenen Maße überdeckt und damit die Fördermenge an Kühlflüssigkeit in den Niedertemperatur-Kühlkreislauf steuert.At the rear of the pump impeller 20, an annular base plate 26 is formed, which a plurality of circumferentially preferably uniformly spaced guide pin 27 (in the sectional drawing Fig. 2 only one guide pin 27 is visible) receives. The guide pins 27 carry or guide a radial wall 21a of the annular slide 21, the peripheral wall 21 b covers the impeller 20b of the pump impeller 20 depending on the ring slide position to a predetermined extent and thus controls the flow rate of cooling liquid in the low-temperature cooling circuit.

Zwischen der Radialwand 21 a 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 Fig. 2 dargestellte, eingefahrene Position vorspannen, in der die zweite Pumpenflut 35 die volle Fördermenge abgibt.Between the radial wall 21 a of the annular slide 21 and the base plate 26 are more, z. B. three circumferentially distributed helical compression springs 28 provided in a preferably same distance, the annular slide 21 in the in the Fig. 2 shown biased retracted position in which the second pump surge 35 emits the full flow rate.

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 21 a des Ringschiebers 21 anliegen.In the hub portion 19b of the pump housing 19 are more, z. B. three circumferentially distributed and preferably a same distance from each other having actuator piston 29 slidably mounted, which rest on a here only extremely schematically illustrated roller bearing pressure ring 30 on the radial wall 21 a of the annular slide 21.

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 adjusting pistons 29 or their bearing bores open into an annular space 19c of the hub portion 19b and can be pressurized via this with coolant from the first pumping flow 34 in a manner to be described further, so that the annular slide 21 is extended into the position reducing the delivery of cooling liquid , For this purpose, a pressure line 31 is connected to the annular space 19c, which is fluidly connected via branch channels 32, 33 in the cylinder housing 1 with the pump chamber 3 and with the first pumping flow 34 for supplying the first cooling circuit in the region of the outflow opening 24. Accordingly, according to this particularly advantageous embodiment, the pump pressure of the first pump flood 34 via the pressure line 31 in the annular space 19c propagate and determined in a simple control manner, the flow rate and the delivery pressure of the second pump surge 35 in the above-described low-temperature circuit.

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 if any faults occur, the second pump surge 35 of the impeller 20 is fully functional or works with the maximum design flow provided.

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 Fig. 2 gezeigten Offenstellung des Ringschiebers 21 z. B. ca. 80% der Fördermenge an Kühlflüssigkeit in den ersten Hauptkühlkreislauf durch die Brennkraftmaschine und ca. 20% in den zweiten Niedertemperatur-Kühlkreislauf mit dem Ladeluftkühler 13 strömen. Selbstverständlich sind für die Offenstellung auch andere Voreinstellungen möglich. Soll demgegenüber die Fördermenge und der Förderdruck des Niedertemparatur-Kühlkreislaufes durch die Ansteuerung des Ringschiebers 21 über den Förderdruck des ersten Kühlkreislaufes und über die Stellkolben 29 vermindert werden kann, der Ringschieber 21 mit dessen Umfangswand 21 b das Flügelrad 20c und dementsprechend die zweite Pumpenflut 35 in vorgegebenem Maße umschließen bzw. abdecken.The pumping floods 34, 35 with the partition wall 20 a in the pump impeller 20 and the partition wall 23 in the pump chamber 3 are structurally z. B. designed so that in the Fig. 2 shown open position of the annular slide 21 z. B. about 80% of the flow rate of cooling fluid in the first main cooling circuit through the engine and about 20% in the second low-temperature cooling circuit with the intercooler 13 flow. Of course, other presets are possible for the open position. If, on the other hand, the flow rate and the delivery pressure of the low-temperature refrigeration circuit can be reduced by controlling the annular slide 21 via the delivery pressure of the first cooling circuit and the adjusting piston 29, the annular slide 21 with its peripheral wall 21 b, the impeller 20 c and accordingly the second pump flood 35 in enclose or cover given dimensions.

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, if necessary, the first pumping flow 34 can also be designed so as to be adjustable in its flow 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 1 a kommunizierenden, den Pumpenraum 3 zumindest teilweise umgebenden Gehäuse angeordnet ist.The second adjusting means may also be formed by an annular slide, the temperature, speed and / or pressure-dependent via a driven by the internal combustion engine pressure medium source, for. is applied hydraulically or pneumatically and is preferably arranged in a communicating with the pump housing or the cylinder housing 1 and / or coolant distributor housing 1 a, the pump chamber 3 at least partially surrounding housing.

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 impeller 20 may optionally be formed by two axially adjacent to each other arranged impellers, which are optionally designed with different outer diameters and / or widths to interpret their flow rates and thus the pump floods accordingly.

BezugszeichenlisteLIST OF REFERENCE NUMBERS

11
Zylindergehäusecylinder housing
1 a1 a
KühlmittelverteilergehäuseCoolant distribution housing
22
Stirnseitefront
33
Pumpenraumpump room
44
Zentrifugalpumpecentrifugal pump
55
Antriebswelledrive shaft
66
Antriebsraddrive wheel
77
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
11 a11 a
Ansaugöffnung Hochtemperatur-KreislaufIntake opening High-temperature circuit
11b11b
Ansaugöffnung Niedertemperatur-KreislaufIntake opening low-temperature circuit
1212
Druckleitungpressure line
1313
LadeluftkühlerIntercooler
1414
RücklaufleitungReturn line
1515
LadeluftleitungTurbo pipe
1616
LadeluftleitungTurbo pipe
17a17a
Leitungmanagement
17b17b
Leitungmanagement
1818
Ausgleichsbehältersurge tank
1919
Gehäusecasing
19a19a
Befestigungsflanschmounting flange
19b19b
Nabenabschnitthub portion
19c19c
Ringraumannulus
2020
Flügelradimpeller
20a20a
Trennwandpartition wall
20b20b
Pumpenflutpump flow
20c20c
Pumpenflutpump flow
2121
Ringschieberannular slide
21 a21 a
Radialwandradial wall
21 b21 b
Umfangswandperipheral wall
2222
Wälzlagerungroller bearing
2323
Trennwandpartition wall
2424
Abströmöffnungoutflow
2525
Abströmöffnungoutflow
2626
Rückwandrear wall
2727
Bolzenbolt
2828
SchraubendruckfedernHelical compression springs
2929
Stellkolbenactuating piston
3030
Druckringpressure ring
3131
Druckleitungpressure line
3232
StichkanalStichkanal
3333
StichkanalStichkanal
3434
erste Pumpenflutfirst pump flood
3535
zweite Pumpenflutsecond pump flood

Claims (13)

Kühlsystem für flüssigkeitsgekühlte Brennkraftmaschinen, insbesondere in Nutz- oder Kraftfahrzeugen, mit einer regelbaren Kühlmittelpumpe und mit einem die Durchflussmenge regelnden Regelelement, dadurch gekennzeichnet, dass die Kühlmittelpumpe (4) mehrflutig mit mehreren jeweils voneinander getrennten Kühlmittelkreisen zugeordneten Pumpenfluten (34, 35) ausgebildet ist, wobei wenigstens eine der Pumpenfluten (35) mittels des Regelelementes (21) hinsichtlich ihrer Förderleistung veränderlich ist.Cooling system for liquid-cooled internal combustion engines, in particular in utility vehicles or motor vehicles, with a controllable coolant pump and with a flow rate regulating control element, characterized in that the coolant pump (4) is formed mehrflutig with a plurality of each separate coolant circuits pump flows (34, 35), wherein at least one of the pumping passages (35) is variable by means of the control element (21) with regard to their delivery rate. Kühlsystem nach Anspruch 1, dadurch gekennzeichnet, dass die Pumpenfluten (34, 35) hinsichtlich ihrer Förderleistung unterschiedlich ausgelegt sind und eine Regelung der Förderleistung wenigstens einer der Pumpenfluten (34, 35) mittels des Regelelementes (21) innerhalb vorgegebener Einstellbereiche erfolgt.Cooling system according to claim 1, characterized in that the pump flows (34, 35) are designed differently in terms of their delivery and a control of the delivery rate of at least one of the pump flows (34, 35) by means of the control element (21) within predetermined adjustment ranges. Kühlsystem nach Anspruch 2, dadurch gekennzeichnet, dass eine erste Pumpenflut (34) ein Kühlsystem der Brennkraftmaschine und eine in der Durchflussmenge veränderliche, zweite Pumpenflut (20c) einen Niedertemperatur-Kreislauf der Brennkraftmaschine versorgt, wobei die erste Pumpenflut (34) auf einen höheren Förderdruck als die zweite Pumpenflut (35) ausgelegt ist, insbesondere durch entsprechende Aufteilung und/oder Auslegung von den Pumpenfluten (34, 35) zugeordneten, zumindest funktionell getrennten Flügelrädern (20b, 20c).Cooling system according to claim 2, characterized in that a first pumping flood (34), a cooling system of the internal combustion engine and a variable in the flow rate, second pumping flow (20c) supplies a low-temperature circuit of the internal combustion engine, wherein the first pumping flow (34) is designed to a higher delivery pressure than the second pumping flow (35), in particular by appropriate division and / or interpretation of the pump flows (34, 35) associated, at least functionally separated impellers (20b, 20c). Kühlsystem nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, dass das Regelelement (21) zur Regulierung der veränderlichen Förderleistung wenigstens einer der Pumpenfluten (35) mittels einer vorgegebenen Menge eines Kühlmittels aus einer anderen, abgetrennten, ersten Pumpenflut (34) beaufschlagbar ist.Cooling system according to one of claims 1 to 3, characterized in that the control element (21) for regulating the variable delivery rate of at least one of the pumping passages (35) can be acted upon by means of a predetermined amount of a coolant from another, separated, first pumping pass (34). Kühlsystem nach Anspruch 4, dadurch gekennzeichnet, dass die beiden Pumpenfluten (34, 35) mittels wenigstens einer Überströmleitung (31) strömungsverbunden sind, wobei die Überströmleitung (31) vorzugsweise als von der Druckseite der das Kühlmittel überpumpenden ersten Pumpenflut (34) abzweigende Druckleitung ausgebildet ist.Cooling system according to claim 4, characterized in that the two pumping passages (34, 35) are flow-connected by means of at least one overflow line (31), the overflow line (31) preferably being designed as a pressure line branching off from the pressure side of the first pumping pass (34) overflowing the coolant is. Kühlsystem nach Anspruch 5, dadurch gekennzeichnet, dass die Überströmleitung (31) in einen dem Regelelement (21) zugeordneten Druckraum (19c) mündet dergestalt, dass das Regelelement (21) entsprechend der in den Druckraum (19c) geförderten Kühlmittelmenge entlang seines vorgegebenen Verstellweges verlagerbar ist und damit die jeweilige hinsichtlich der Förderleistung veränderbare Pumpenflut (35) vollständig freigibt oder wenigstens teilweise verschließt.Cooling system according to claim 5, characterized in that the overflow line (31) in a the control element (21) associated pressure chamber (19c) opens such that the control element (21) according to the in the pressure chamber (19c) promoted amount of coolant along its predetermined displacement displaced is and thus the respective variable with respect to the flow rate pumping flood (35) completely free or at least partially closes. Kühlsystem nach Anspruch 6, dadurch gekennzeichnet, dass die Überströmleitung (31) in einem als Ringraum um eine Antriebswelle (5) der Pumpe herum ausgebildeten Druckraum (19c) zwischen dem Pumpengehäuse (19) und dem als Ringschieber ausgebildeten Regelelement (21) mündet.Cooling system according to Claim 6, characterized in that the overflow line (31) opens into a pressure chamber (19c) formed as an annular space around a drive shaft (5) of the pump between the pump housing (19) and the control element (21) designed as an annular slide. Kühlsystem nach einem der Ansprüche 1 bis 7, dadurch gekennzeichnet, dass die hinsichtlich ihrer Förderleistung veränderbare, wenigstens eine Pumpenflut (20c) in ihrer Förderleistung so ausgelegt ist, dass bei voller Förderleistung ein definierter Pumpendruck im zugeordneten Kühlmittelkreis nicht überschritten wird.Cooling system according to one of claims 1 to 7, characterized in that the variable in terms of their capacity, at least one pumping flood (20c) is designed in its capacity so that at full capacity, a defined pump pressure in the associated coolant circuit is not exceeded. Kühlsystem nach einem der Ansprüche 1 bis 8, dadurch gekennzeichnet, dass die Pumpenfluten (34, 35) im Pumpenraum (3) mittels einer vorzugsweise integraler Bestandteil eines Pumpengehäuses (19) bildenden Trennwand (23) voneinander vollständig oder unter Vorsehen von Leckagen definierter Größenordnung voneinander im wesentlichen getrennt sind.Cooling system according to one of claims 1 to 8, characterized in that the pump flows (34, 35) in the pump chamber (3) by means of a preferably integral part of a pump housing (19) forming the partition (23) from each other completely or with provision of leakage defined order from each other are essentially separated. Kühlsystem nach einem der Ansprüche 1 bis 9, dadurch gekennzeichnet, dass den Pumpenfluten (34, 35) jeweils ein separates Flügelrad (20b, 20c) eines Pumpenlaufrades (20) zugeordnet ist.Cooling system according to one of claims 1 to 9, characterized in that the pump flows (34, 35) are each assigned a separate impeller (20b, 20c) of a pump impeller (20). Kühlsystem nach Anspruch 10, dadurch gekennzeichnet, dass die Flügelräder (20b, 20c) auf einer gemeinsamen Antriebswelle (5) der Kühlmittelpumpe angeordnet und von dieser angetrieben sind.Cooling system according to claim 10, characterized in that the impellers (20b, 20c) are arranged on a common drive shaft (5) of the coolant pump and driven by the same. Kühlsystem nach einem der Ansprüche 1 bis 11, dadurch gekennzeichnet, dass die unterschiedlichen Kühlmittelkreise bzw. Pumpenfluten (34, 35) an einen Ausgleichsbehälter (18) angeschlossen sind.Cooling system according to one of claims 1 to 11, characterized in that the different coolant circuits or pump flows (34, 35) are connected to a surge tank (18). Kühlsystem nach einem der Ansprüche 4 bis 12, dadurch gekennzeichnet, dass auch die erste Pumpenflut (34) über ein zweites Verstellmittel in ihrer Fördermenge verstellbar ausgeführt ist.Cooling system according to one of claims 4 to 12, characterized in that the first pumping flow (34) is adjustable in its flow rate via a second adjusting means.
EP09009316.2A 2008-09-27 2009-07-17 Cooling system for vehicles with fluid-cooled combustion engine Active EP2169233B1 (en)

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Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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
WO2012116676A1 (en) * 2011-03-02 2012-09-07 Geräte- und Pumpenbau GmbH Dr. Eugen Schmidt Controllable coolant pump
FR2978207A1 (en) * 2011-07-18 2013-01-25 Schaeffler Technologies Ag COOLING AGENT PUMP FOR A COOLING CIRCUIT OF AN INTERNAL COMBUSTION ENGINE
WO2013034126A1 (en) * 2011-09-09 2013-03-14 Geräte- und Pumpenbau GmbH Dr. Eugen Schmidt Controllable coolant pump
CN103459798A (en) * 2011-03-04 2013-12-18 欧根·施密特博士仪器和泵制造有限责任公司 Controllable cooling system for a motor vehicle, coolant pump therefor, impeller for use in the coolant pump, and method for controlling a coolant flow in such a cooling system
CN103591020A (en) * 2012-08-14 2014-02-19 斯瓦本冶炼厂汽车股份有限公司 Rotary pump with adjustable delivery volume, especially for adjusting a coolant pump
EP2455615A3 (en) * 2010-11-19 2014-04-09 MAHLE International GmbH Pump
DE102014009367B3 (en) * 2014-06-21 2015-03-05 Geräte- und Pumpenbau GmbH Dr. Eugen Schmidt Adjustable coolant pump
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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DE102010025560B4 (en) 2010-06-30 2019-03-07 Iav Gmbh Ingenieurgesellschaft Auto Und Verkehr Switchable coolant pump
DE102010046316B4 (en) * 2010-09-23 2020-03-19 Audi Ag Pump drive with viscous coupling and mechanical speed control
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
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

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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

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Cited By (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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
CN102477996B (en) * 2010-11-19 2016-03-30 马勒国际有限公司 Pump
EP2455615A3 (en) * 2010-11-19 2014-04-09 MAHLE International GmbH Pump
WO2012116676A1 (en) * 2011-03-02 2012-09-07 Geräte- und Pumpenbau GmbH Dr. Eugen Schmidt Controllable coolant pump
CN103459798B (en) * 2011-03-04 2016-03-16 尼得科Gpm有限公司 The method of the cooling system of vehicle, coolant pump, impeller and controlled cooling model liquid stream
CN103459798A (en) * 2011-03-04 2013-12-18 欧根·施密特博士仪器和泵制造有限责任公司 Controllable cooling system for a motor vehicle, coolant pump therefor, impeller for use in the coolant pump, and method for controlling a coolant flow in such a cooling system
FR2978207A1 (en) * 2011-07-18 2013-01-25 Schaeffler Technologies Ag COOLING AGENT PUMP FOR A COOLING CIRCUIT OF AN INTERNAL COMBUSTION ENGINE
WO2013034126A1 (en) * 2011-09-09 2013-03-14 Geräte- und Pumpenbau GmbH Dr. Eugen Schmidt Controllable coolant pump
US20140212267A1 (en) * 2011-09-09 2014-07-31 Geraete- Und Pumpenbau Gmbh Dr. Eugen Schmidt Controllable coolant pump
US9528521B2 (en) 2011-09-09 2016-12-27 Nidec Gpm Gmbh Controllable coolant pump
CN103591020A (en) * 2012-08-14 2014-02-19 斯瓦本冶炼厂汽车股份有限公司 Rotary pump with adjustable delivery volume, especially for adjusting a coolant pump
DE102014009367B3 (en) * 2014-06-21 2015-03-05 Geräte- und Pumpenbau GmbH Dr. Eugen Schmidt Adjustable coolant pump
WO2015192820A1 (en) 2014-06-21 2015-12-23 Nidec Gpm Gmbh Adjustable coolant pump
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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DE102008049204A1 (en) 2010-04-01
EP2169233A3 (en) 2017-03-29

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