EP3371464B1 - Method for controlling a mechanically controllable coolant pump for an internal combustion engine - Google Patents

Method for controlling a mechanically controllable coolant pump for an internal combustion engine Download PDF

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Publication number
EP3371464B1
EP3371464B1 EP16787373.6A EP16787373A EP3371464B1 EP 3371464 B1 EP3371464 B1 EP 3371464B1 EP 16787373 A EP16787373 A EP 16787373A EP 3371464 B1 EP3371464 B1 EP 3371464B1
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EP
European Patent Office
Prior art keywords
internal combustion
combustion engine
coolant
controlling
control slide
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EP16787373.6A
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German (de)
French (fr)
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EP3371464A1 (en
Inventor
Stephan Zielberg
Andreas Burger
Michael-Thomas Benra
Stefan Rothgang
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Pierburg GmbH
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Pierburg GmbH
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    • 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
    • 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
    • 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
    • F01P2023/00—Signal processing; Details thereof
    • F01P2023/08—Microprocessor; Microcomputer
    • 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
    • F01P2037/00—Controlling
    • F01P2037/02—Controlling starting

Definitions

  • the invention relates to a method for controlling a mechanically controllable coolant pump for an internal combustion engine, in which coolant is conveyed via a coolant pump impeller into a conveying channel surrounding the coolant pump impeller and to a pump outlet, wherein the delivery depends on the position of an adjustable control slide, via which a flow cross section an annular gap between an outlet of the coolant pump impeller and the surrounding conveyor channel is controlled, and wherein a first pressure space on a first axial side of the control slide is filled with pressurized coolant to reduce the pumped to the pump outlet flow rate by reducing the flow cross-section.
  • Coolant pumps are used in internal combustion engines to control the amount of subsidized coolant in order to prevent overheating of the internal combustion engine.
  • the drive of these pumps is usually via a belt or chain drive, so that thedeffenpumpenrad is driven by the speed of the crankshaft or a fixed ratio to the speed of the crankshaft.
  • the pumped coolant quantity is to be adapted to the coolant requirement of the internal combustion engine or of the motor vehicle.
  • the cold running phase of the engine should be shortened. This is done inter alia by the fact that the coolant flow is throttled or completely shut off during this phase.
  • Such a coolant pump with a secondary pump acting as a secondary pump is from the DE 10 2012 207 387 A1 known.
  • a pressure side of the secondary pump is closed by a 3/2-way valve in a first position and a suction side of the pump connected to the cooling circuit and the slider and connected in a second position, the pressure side with the slide and the suction side with the cooling circuit.
  • a spring which may possibly be waived by a reset of the pump should be made by the resulting negative pressure on the suction port.
  • a second pressure chamber is filled at a first side axially opposite side of the control slide with pressurized coolant and when switching off the engine, the control slide in a defined, dependent on the coolant temperature position is moved, in which the control slide remains until the engine starts, depending on the operating condition can be set in advance an expected coolant flow demand, which is effective immediately at start.
  • the control slide When the internal combustion engine is switched off, the control slide is preferably moved into a position closing the annular gap when the coolant temperature is below a defined one Threshold is. This has the consequence that no coolant flow is present at the start of the internal combustion engine, whereby a rapid heating is achieved. Furthermore, this position ensures that in the stance phase no coolant flow is produced by the thermosiphon effect, which, for example, would lead to a renewed cooling of the internal combustion engine in a late period of the cold start phase.
  • control slide is moved when switching off the internal combustion engine in a position completely opening the annular gap when the coolant temperature is equal to the defined threshold or above the defined threshold.
  • the threshold value preferably corresponds to a desired value defined in an engine control for the operating temperature of the coolant during operation of the internal combustion engine. This is thus the value to which the coolant is to be adjusted during operation of the vehicle by the engine control, on the one hand to achieve good lubrication and on the other hand to avoid overheating. In a conventional motor vehicle, such a threshold value would be set at about 95 ° C, for example.
  • control takes place when switching off the internal combustion engine by switching off the ignition of the engine. Accordingly, an optimal coolant flow when parking the vehicle for the next start can be preset.
  • control slide is accordingly moved when stopped in a position in which overheating or unwanted cooling can be prevented by the slide when stopping according to the temperature either closed or opened.
  • a similar control is preferably also in a sailing operation of the vehicle in which the engine is switched off and generates no heat of combustion accordingly. In this state as well, undesirable cooling or heating depending on the operating temperature can be prevented.
  • the opening of the annular gap is effected by a progressive pressure increase in the second pressure chamber.
  • This progressive increase in pressure leads to a slow and continuous opening of the control slide, whereby a sudden cold water surge is prevented, which could lead to a sudden cooling of the crankcase.
  • the threshold value for the coolant temperature is stored as a function of the ambient temperature in a characteristic map. Accordingly, the threshold value can be set higher for colder ambient temperatures, since a stronger cooling occurs when the internal combustion engine is switched off even without the thermosiphon effect occurring.
  • the desired regulation is particularly simple if, depending on the position of a 3/2-way solenoid valve, one of the pressure chambers is pressurized with pressurized coolant and the 3/2-way solenoid valve is activated when the internal combustion engine is switched off, in order to control the control slide to move to the required position.
  • a short signal when stopping the control slide can be quickly moved to the desired position.
  • a method for controlling a mechanically controllable coolant pump for an internal combustion engine in which a pre-adjustment of the control slide is already made when stopping the engine for optimal restart, on the one hand overheating is prevented by a sufficient coolant flow is ensured and on the other hand too fast cooling of the engine is prevented.
  • the control slide is at start in the then optimal position to shorten warm-up phases.
  • FIG. 1 shows a side view of a coolant pump according to the invention in a sectional view.
  • the illustrated coolant pump consists of an outer housing 10, in which a spiral conveying channel 12 is formed, into which a coolant is sucked in via an axial pump inlet 14 likewise formed in the outer housing 10, which coolant flows via the delivery channel 12 to a tangential pump outlet 16 and formed in the outer housing 10 is conveyed into a cooling circuit of the internal combustion engine.
  • a coolant pump impeller 20 is fixed radially inside the conveying channel 12 on a drive shaft 18, which is designed as a Radialpumpenrad, by the rotation of the promotion of the coolant takes place in the conveying channel 12.
  • a control pump impeller 22 is formed, which is rotated in accordance with the coolant pump impeller 20.
  • This control pump impeller 22 has blades 24, which are arranged axially opposite to a flow channel 26 designed as a side channel, which is formed in a first inner housing part 28.
  • a non-visible inlet and an outlet 30 are formed, so that the control pump impeller 22 forms a control pump 32 with the flow channel 26, via which the pressure of the coolant from the inlet to the outlet 30 is increased.
  • a drive via a chain drive would also be possible.
  • the pulley 36 is mounted on a second housing part 40 via a double-row ball bearing 38.
  • the second housing part 40 has an inner axial passage opening 42 into which an annular projection 44 of the first housing part 28 projects, via which the first housing part 28 is fastened to the second housing part 40.
  • the second housing part 40 is under Interposed layer of a seal 46 attached to the outer housing 10.
  • the outer housing 10 at its pump inlet 14 opposite axial end a receiving opening 48 into which an annular projection 50 of the second housing part 40 projects.
  • the annular projection 50 also serves as a rear stop 52 for a control slide 54, the cylindrical peripheral wall 56 can be pushed over the coolant pump impeller 20 so that a free cross section of an annular gap 58 between an outlet 60 of the coolant pump impeller 20 and the delivery channel 12 is controlled. In accordance with the position of this control slide 54, the coolant flow conveyed through the coolant circuit is thus regulated.
  • the control slide 54 has, in addition to the peripheral wall 56, a bottom 62 with an inner opening 64, from the outer periphery of which the circumferential wall 56 extends axially through an annular gap 66 between the first housing part 28 and the outer housing 10 in the direction of the axially adjoining annular gap 58 , On the inner periphery and on the outer circumference of the bottom 62, a piston ring 68 is arranged in each case in a radial groove, via which the control slide 54 is slidably mounted in the radially inner region on the first housing part 28 and in the radially outer region in the annular projection 50 of the second housing part 40 ,
  • a first pressure chamber 70 axially through the second housing part 40 and the bottom 62 of the control slide 54 and radially outwardly through the outer housing 10 and the annular projection 50 of the second housing part 40 and after is limited radially inwardly by the first housing part 28.
  • a second pressure chamber 72 is formed, which extends axially through the bottom 62 and the first housing part 28, radially outwardly through the peripheral wall 56 of Control slide 54 and radially inwardly limited by the first housing part 28.
  • the peripheral wall 56 of the control slide 54 in accordance with the annular gap 58 hinein- or pushed out of the annular gap 58.
  • the required pressure difference is generated by the control pump 32 and by means of a valve 74, which is designed as a 3/2-way solenoid valve, the respective pressure chamber 70, 72, respectively.
  • a receiving opening 76 for the valve 74 is formed in the second housing part 40, via which, depending on the position of its closing body 78, a flow cross-section 80 of a pressure channel 82 is controlled.
  • This pressure channel 82 extends from the outlet 30 of the flow channel 26 of the control pump 32 to the first pressure chamber 70.
  • the second pressure chamber 72 is connected via a connecting channel, which is formed in the first housing part 28, with the flow channel 26, said connecting channel formed by a bore is that extends from a region of the inlet from the flow channel 26 directly into the second pressure chamber.
  • a third, not shown, flow connection of the control valve leads to the suction side of the coolant pump.
  • the annular gap 58 at the outlet 60 of the coolant pump impeller 20 is fully released by the solenoid valve 74 is not energized, whereby the closing body 78 is moved due to a spring force in its the flow cross-section 80 of the pressure channel 82 occlusive position , As a result, no pressure is built up by the coolant in the first pressure chamber 70, but the coolant present in the pressure chamber 70 can flow to the pump inlet 14 of the coolant pump via the not shown other flow connection of the solenoid valve 74, which is released in this state.
  • the solenoid valve 74 is energized, whereby the closing body 78 releases the flow cross-section 80 of the pressure channel 82. Accordingly, the pressure generated at the outlet of the control pump 32 is also generated in the pressure channel 82 and in the first pressure chamber 70, while at the same time the pressure in the second pressure chamber 72 decreases, since in the region of the inlet by the suction of the coolant, a reduced pressure. In this case, the coolant present in the second pressure chamber 72 is initially aspirated. In this state, again corresponding to a pressure difference at the bottom 62 of the control slide 54, which causes the control slide 54 is moved into the annular gap 58 and thus the flow of coolant in the cooling circuit is interrupted.
  • a solenoid valve 74 which is designed as a proportional valve or clocked valve with a variable duty cycle, used, it is also possible to drive the valve 74 in intermediate positions, whereby for each position of the control slide 54, a balance of forces can be achieved, so that a complete control of Throughflow cross section of the annular gap 58 is made possible.
  • the solenoid valve 74 is not energized, whereby the pressure in the second pressure chamber 72 increases and the control slide 54 in its annular gap 58 releasing position is moved.
  • the coolant continues to circulate due to the thermosiphon effect and thus absorbs further heat from the still hot combustion engine.
  • the reverse path can also be taken for this shutdown and the control slide 54 are moved by energizing the solenoid valve 74 in its closing the annular gap 58 position. This has the consequence that a longer life, a cooling begins, but the amount of heat is stored a little longer.
  • the Regulator valve 54 At a following start would be the Regulator valve 54 in its occluding position, so that a rapid re-heating of the coolant to shorten the warm-up phase would take place.
  • the control slide 54 Whether the control slide 54 is moved when switching off the ignition in its open or closed position, for example, depending on the outside temperature can be decided. At particularly high temperatures, the control slide 54 would then rather moved into the open state, to ensure sufficient heat dissipation and thus to prevent overheating of the engine.
  • a corresponding regulation can also be made for vehicles with an automatic start-stop system. If the engine is turned off in the start-stop mode, the control slide 54 should be moved depending on the current coolant temperature in the opening state of the annular gap 58, when the operating temperature is reached and thus the threshold is exceeded, since only short life is to be assumed in where no great cooling is to be expected, however, an overheating of the coolant could be done by the warm engine. Accordingly, in the parked state, circulation takes place through the thermosiphon effect. When starting the engine, the control slide is then in this position, so that again can take place without time delay again maximum coolant delivery. If the operating temperature has not yet been reached, the control slide 54 is left when switching off in the annular gap 58 occlusive state or moved into this.
  • a corresponding regulation should also take place during the sailing operation of the motor vehicle, in which the internal combustion engine is disconnected from the drive train and switched off. After switching off the internal combustion engine, the energization of the valve 74 can then be terminated without the control slide 54 being displaced when the engine is switched off. After re-starting the engine, the known demand-dependent control of the control slide takes place. This following control can be done either via a closed loop with a bearing feedback of the control slide or performed without sensors.
  • Such a method allows on the one hand a control of the coolant flow with the vehicle parked within the physically existing limits and an optimal position of the control slide and thus the coolant flow immediately during the starting process of the vehicle, whereby the cold running phase can be shortened. Overall, the existing amounts of heat can be used better and yet overheating safely avoided in all operating conditions.

Description

Die Erfindung betrifft ein Verfahren zur Regelung einer mechanisch regelbaren Kühlmittelpumpe für eine Verbrennungskraftmaschine, bei dem Kühlmittel über ein Kühlmittelpumpenlaufrad in einen das Kühlmittelpumpenlaufrad umgebenden Förderkanal und zu einem Pumpenauslass gefördert wird, wobei die Förderung abhängig ist von der Position eines verstellbaren Regelschiebers, über den ein Durchströmungsquerschnitt eines Ringspalts zwischen einem Austritt des Kühlmittelpumpenlaufrades und dem umgebenden Förderkanal geregelt wird, und wobei zur Reduzierung des zum Pumpenauslass geförderten Kühlmittelvolumenstroms durch Verkleinerung des Durchströmungsquerschnitts ein erster Druckraum an einer ersten axialen Seite des Regelschiebers mit unter Druck stehendem Kühlmittel gefüllt wird.The invention relates to a method for controlling a mechanically controllable coolant pump for an internal combustion engine, in which coolant is conveyed via a coolant pump impeller into a conveying channel surrounding the coolant pump impeller and to a pump outlet, wherein the delivery depends on the position of an adjustable control slide, via which a flow cross section an annular gap between an outlet of the coolant pump impeller and the surrounding conveyor channel is controlled, and wherein a first pressure space on a first axial side of the control slide is filled with pressurized coolant to reduce the pumped to the pump outlet flow rate by reducing the flow cross-section.

Kühlmittelpumpen dienen in Verbrennungsmotoren zur Mengenregelung des geförderten Kühlmittels, um ein Überhitzen des Verbrennungsmotors zu verhindern. Der Antrieb dieser Pumpen erfolgt zumeist über einen Riemen- oder Kettentrieb, so dass das Kühlmittelpumpenrad mit der Drehzahl der Kurbelwelle oder einem festen Verhältnis zur Drehzahl der Kurbelwelle angetrieben wird.Coolant pumps are used in internal combustion engines to control the amount of subsidized coolant in order to prevent overheating of the internal combustion engine. The drive of these pumps is usually via a belt or chain drive, so that the Kühlmittelpumpenrad is driven by the speed of the crankshaft or a fixed ratio to the speed of the crankshaft.

In modernen Verbrennungsmotoren ist die geförderte Kühlmittelmenge an den Kühlmittelbedarf des Verbrennungsmotors oder des Kraftfahrzeugs anzupassen. Zur Vermeidung erhöhter Schadstoffemissionen und Minderung des Kraftstoffverbrauchs sollte insbesondere die Kaltlaufphase des Motors verkürzt werden. Dies erfolgt unter anderem dadurch, dass der Kühlmittelstrom während dieser Phase gedrosselt oder vollkommen abgeschaltet wird.In modern internal combustion engines, the pumped coolant quantity is to be adapted to the coolant requirement of the internal combustion engine or of the motor vehicle. To avoid increased pollutant emissions and reduction of fuel consumption, in particular the cold running phase of the engine should be shortened. This is done inter alia by the fact that the coolant flow is throttled or completely shut off during this phase.

Zur Regelung der Kühlmittelmenge sind verschiedene Pumpenausführungen bekannt geworden. Neben elektrisch angetriebenen Kühlmittelpumpen sind Pumpen bekannt, die über Kupplungen, insbesondere hydrodynamische Kupplungen an ihren Antrieb angekoppelt oder von diesem getrennt werden können. Eine besonders kostengünstige und einfach aufgebaute Möglichkeit zur Regelung des geförderten Kühlmittelstroms ist die Verwendung eines axial verschiebbaren Regelschiebers, der über das Kühlmittelpumpenlaufrad geschoben wird, so dass zur Reduzierung des Kühlmittelstroms die Pumpe nicht in den umliegenden Förderkanal sondern gegen den geschlossenen Schieber fördert.To control the amount of coolant various pump designs have become known. In addition to electrically driven coolant pumps pumps are known which can be coupled via couplings, in particular hydrodynamic couplings to their drive or separated from it. A particularly cost-effective and simply constructed possibility for controlling the conveyed coolant flow is the use of an axially displaceable control slide, which is pushed over the coolant pump impeller, so that promotes the reduction of the coolant flow, the pump not in the surrounding conveyor channel but against the closed slide.

Die Regelung dieser Schieber erfolgt ebenfalls in unterschiedlicher Weise. Neben einer rein elektrischen Verstellung hat sich vor allem eine hydraulische Verstellung der Schieber bewährt. Diese erfolgt zumeist über einen ringförmigen Kolbenraum, der mit einer Hydraulikflüssigkeit gefüllt wird, und dessen Kolben mit dem Schieber verbunden ist, so dass bei Füllung des Raumes der Schieber über das Laufrad verschoben wird. Eine Rückstellung des Schiebers erfolgt durch Öffnen des Kolbenraums zu einem Auslass, was zumeist über ein Magnetventil erfolgt sowie unter Einwirkung einer Feder, die die Kraft zur Rückstellung des Schiebers zur Verfügung stellt.The regulation of these slides also takes place in different ways. In addition to a purely electrical adjustment, especially a hydraulic adjustment of the slide has proven. This is usually done via an annular piston chamber which is filled with a hydraulic fluid, and whose piston is connected to the slider, so that when the space is filled, the slider is moved over the impeller. A return of the slide takes place by opening the piston chamber to an outlet, which is usually done via a solenoid valve and under the action of a spring which provides the force to return the slider.

Um die zum Verfahren des Schiebers benötigte Kühlmittelmenge nicht über zusätzliche Fördereinheiten, wie zusätzliche Kolben/Zylindereinheiten zur Verfügung stellen zu müssen oder andere Hydraulikflüssigkeiten zur Betätigung verdichten zu müssen, sind mechanisch regelbare Kühlmittelpumpen bekannt geworden, auf deren Antriebswelle ein zweites Förderrad angeordnet ist, über welches der Druck zur Verstellung des Schiebers zur Verfügung gestellt wird. Diese Pumpen werden beispielsweise als Seitenkanalpumpen oder Servopumpen ausgeführt.In order not to have to provide the necessary for the process of the slide coolant amount on additional conveyor units, such as additional piston / cylinder units or compress other hydraulic fluids for actuation, mechanically controllable coolant pumps have become known on the drive shaft, a second impeller is arranged, via which the pressure for adjusting the slider is provided. This Pumps are designed, for example, as side channel pumps or servo pumps.

Eine derartige Kühlmittelpumpe mit einer als Sekundärpumpe wirkenden Seitenkanalpumpe ist aus der DE 10 2012 207 387 A1 bekannt. Bei dieser Pumpe wird über ein 3/2-Wegeventil in einer ersten Stellung eine Druckseite der Sekundärpumpe verschlossen und eine Saugseite der Pumpe mit dem Kühlkreislauf und dem Schieber verbunden und in einer zweiten Stellung die Druckseite mit dem Schieber und die Saugseite mit dem Kühlkreislauf verbunden. Zur Rückstellung des Schiebers dient eine Feder, auf die eventuell verzichtet werden können soll, indem durch den am Sauganschluss entstehenden Unterdruck eine Rückstellung der Pumpe erfolgen soll.Such a coolant pump with a secondary pump acting as a secondary pump is from the DE 10 2012 207 387 A1 known. In this pump, a pressure side of the secondary pump is closed by a 3/2-way valve in a first position and a suction side of the pump connected to the cooling circuit and the slider and connected in a second position, the pressure side with the slide and the suction side with the cooling circuit. To reset the slide is a spring, which may possibly be waived by a reset of the pump should be made by the resulting negative pressure on the suction port.

Problematisch ist es jedoch, dass beim Starten des Verbrennungsmotors zunächst kein ausreichender Kühlmitteldruck vorhanden ist, um den Regelschieber schnell in seine den Kanal verschließende Stellung zu verschieben und so einen Kühlmittelstrom zu unterbinden. Eine schnelle Regelung des Kühlmittelstroms ist somit unmittelbar nach dem Starten insbesondere bei Leerlaufdrehzahl nicht möglich, wodurch die Aufheizzeiten nicht so stark gekürzt werden können, wie bei einer unmittelbaren Abschaltung durch Verschieben des Regelschiebers in den Ringspalt.The problem, however, is that when starting the engine initially no sufficient coolant pressure is present to quickly move the control slide in its closing the channel position and thus to prevent a coolant flow. A quick control of the coolant flow is therefore not possible immediately after starting, especially at idle speed, whereby the heating can not be reduced as much as in an immediate shutdown by moving the control slide in the annular gap.

Daher wird für Fahrzeuge mit Start- Stop-Automatik in mehreren Schriften eine Lösung vorgeschlagen, bei der zusätzlich zu einer mechanisch angetriebenen Pumpe eine Elektropumpe im Kühlmittelkreislauf angeordnet wird, um eine Förderung des Kühlmittels bei hohen Kühlmitteltemperaturen auch bei geringen Drehzahlen aufrecht erhalten zu können. Eine derartige Anordnung ist beispielsweise aus der WO 2012/119622A2 bekannt. Beim dort offenbarten Kühlsystem soll der Regelschieber zur Verhinderung einer unerwünschten Abkühlung beim Start in seine den Kanal verschließende Stellung verfahren werden. Dies funktioniert jedoch nur mit elektrisch betriebenen Aktoren, da bei Leerlaufdrehzahl in der Regel kein ausreichender hydraulischer Druck zur Verschiebung des Regelschiebers vorliegt.Therefore, a solution is proposed for vehicles with automatic start / stop in several writings, in which in addition to a mechanically driven pump, an electric pump in the coolant circuit is arranged to maintain delivery of the coolant at high coolant temperatures even at low speeds can. Such an arrangement is for example from the WO 2012 / 119622A2 known. In the cooling system disclosed therein, the control slide to prevent unwanted cooling at startup in its closing the channel position is to be moved. This However, only works with electrically operated actuators, since at idle speed usually no sufficient hydraulic pressure to move the control slide is present.

Es stellt sich daher die Aufgabe, ein Verfahren zur Regelung einer mechanisch regelbaren Kühlmittelpumpe für eine Verbrennungskraftmaschine bereit zu stellen, bei dem mit einer einzigen Kühlmittelpumpe sowohl eine schnelle, verzögerungsfreie Aufheizung des Verbrennungsmotors als auch ein ausreichender Kühlmittelstrom zur Verhinderung einer Überhitzung sichergestellt werden können.It is therefore the object to provide a method for controlling a mechanically controllable coolant pump for an internal combustion engine, in which both a rapid, instantaneous heating of the engine and a sufficient coolant flow to prevent overheating can be ensured with a single coolant pump.

Diese Aufgabe wird durch ein Verfahren zur Regelung einer mechanisch regelbaren Kühlmittelpumpe mit den Merkmalen des Hauptanspruchs 1 gelöst.This object is achieved by a method for controlling a mechanically controllable coolant pump with the features of the main claim 1.

Dadurch, dass zur Erhöhung des zum Pumpenauslass geförderten Kühlmittelvolumenstroms durch Vergrößerung des Durchströmungsquerschnitts ein zweiter Druckraum an einer zur ersten Seite axial gegenüberliegenden Seite des Regelschiebers mit unter Druck stehendem Kühlmittel gefüllt wird und beim Abschalten des Verbrennungsmotors der Regelschieber in eine definierte, von der Kühlmitteltemperatur abhängige Position verfahren wird, in der der Regelschieber bis zum Motorstart verbleibt, kann in Abhängigkeit des jeweiligen Betriebszustandes vorab ein zu erwartender Kühlmittelstrombedarf eingestellt werden, der sofort beim Start wirksam ist. Dies funktioniert durch die rein hydraulische Betätigung des Regelschiebers auf den keine ständig wirksamen Kräfte wie Federkräfte einwirken. Entsprechend behält der Regelschieber die beim Abschalten gewählte Position bis zum nächsten Motorstart immer bei.Characterized in that, to increase the pumped to the pump outlet flow rate by increasing the flow cross section, a second pressure chamber is filled at a first side axially opposite side of the control slide with pressurized coolant and when switching off the engine, the control slide in a defined, dependent on the coolant temperature position is moved, in which the control slide remains until the engine starts, depending on the operating condition can be set in advance an expected coolant flow demand, which is effective immediately at start. This works by the purely hydraulic actuation of the control slide on which no constantly acting forces such as spring forces act. Accordingly, the control slide always retains the position selected during switch-off until the next engine start.

Vorzugsweise wird der Regelschieber beim Abschalten des Verbrennungsmotors in eine den Ringspalt verschließende Position verfahren, wenn die Kühlmitteltemperatur unter einem definierten Schwellwert liegt. Dies hat zur Folge, dass beim Start des Verbrennungsmotors kein Kühlmittelstrom vorliegt, wodurch eine schnelle Aufheizung erreicht wird. Des Weiteren wird durch diese Stellung sichergestellt, dass in der Standphase kein Kühlmittelstrom durch den Thermosiphoneffekt entsteht, der beispielsweise in einem späten Zeitraum der Kaltstartphase zu einem erneuten Abkühlen des Verbrennungsmotors führen würde.When the internal combustion engine is switched off, the control slide is preferably moved into a position closing the annular gap when the coolant temperature is below a defined one Threshold is. This has the consequence that no coolant flow is present at the start of the internal combustion engine, whereby a rapid heating is achieved. Furthermore, this position ensures that in the stance phase no coolant flow is produced by the thermosiphon effect, which, for example, would lead to a renewed cooling of the internal combustion engine in a late period of the cold start phase.

Zusätzlich ist es vorteilhaft, wenn der Regelschieber beim Abschalten des Verbrennungsmotors in eine den Ringspalt vollständig öffnende Position verfahren wird, wenn die Kühlmitteltemperatur dem definierten Schwellwert entspricht oder oberhalb des definierten Schwellwertes liegt. Diese Regelung hat zur Folge, dass ein Überhitzen beim Neustart nicht erfolgen kann, da sofort selbst bei Leerlauf ein ausreichender Kühlmittelstrom zur Verfügung steht, da die Kühlmittelpumpe frei fördern kann und während des Stillstandes durch den Thermosiphoneffekt eine zusätzliche Abkühlung des Motors erfolgt.In addition, it is advantageous if the control slide is moved when switching off the internal combustion engine in a position completely opening the annular gap when the coolant temperature is equal to the defined threshold or above the defined threshold. This regulation has the consequence that overheating during the restart can not take place, since a sufficient coolant flow is immediately available even at idle, since the coolant pump can freely convey and an additional cooling of the engine takes place during standstill due to the thermosiphon effect.

Dabei entspricht der Schwellwert vorzugsweise einem in einer Motorsteuerung definierten Sollwert für die Betriebstemperatur des Kühlmittels im Betrieb des Verbrennungsmotors. Dies ist somit der Wert, auf den das Kühlmittel im laufenden Betrieb des Fahrzeugs durch die Motorsteuerung eingeregelt werden soll, um einerseits eine gute Schmierung zu erreichen und andererseits ein Überhitzen zu vermeiden. Bei einem üblichen Kraftfahrzeug wäre ein solcher Schwellwert beispielsweise bei etwa 95°C anzusetzen.In this case, the threshold value preferably corresponds to a desired value defined in an engine control for the operating temperature of the coolant during operation of the internal combustion engine. This is thus the value to which the coolant is to be adjusted during operation of the vehicle by the engine control, on the one hand to achieve good lubrication and on the other hand to avoid overheating. In a conventional motor vehicle, such a threshold value would be set at about 95 ° C, for example.

Vorzugsweise erfolgt die Regelung beim Abschalten des Verbrennungsmotors durch Abstellen der Zündung des Verbrennungsmotors. Entsprechend kann ein optimaler Kühlmittelstrom beim Abstellen des Fahrzeugs für den nächsten Start voreingestellt werden.Preferably, the control takes place when switching off the internal combustion engine by switching off the ignition of the engine. Accordingly, an optimal coolant flow when parking the vehicle for the next start can be preset.

Neben den beschriebenen Verfahren zur Regelung wäre es in diesem Zustand auch vorteilhaft, unabhängig von der vorhandenen Kühlmitteltemperatur beim Abstellen der Zündung des Verbrennungsmotors den Regelschieber in eine den Ringspalt verschließende Position zu verfahren. In diesem Zustand verlässt der Fahrer üblicherweise für einen kürzeren oder längeren Zeitraum das Fahrzeug, so dass aufgrund des längeren Stehens des Fahrzeugs ohnehin eine ausreichende Abkühlung stattfinden wird. Dies ist insbesondere dann der Fall, wenn geringe Umgebungstemperaturen vorliegen. Beim Neustart des Fahrzeugs wäre dies dann für den Kaltstart voreingestellt, so dass die Aufheizphase verkürzt würde.In addition to the described method for control, it would also be advantageous in this state, regardless of the existing coolant temperature when stopping the ignition of the engine to move the control slide in an annular gap closing position. In this state, the driver usually leaves the vehicle for a shorter or longer period, so that due to the longer standing of the vehicle anyway a sufficient cooling will take place. This is especially the case when low ambient temperatures are present. When the vehicle is restarted, this would then be preset for the cold start, so that the heating phase would be shortened.

Des Weiteren ist es vorteilhaft, wenn die Regelung beim Abschalten des Verbrennungsmotors im Start-Stopp-Betrieb erfolgt. Der Regelschieber wird entsprechend beim Stop in eine Position verfahren, in der ein Überhitzen oder eine unerwünschte Abkühlung verhindert werden, indem der Schieber beim Stoppen entsprechend der Temperatur entweder geschlossen oder geöffnet wird.Furthermore, it is advantageous if the control takes place when switching off the internal combustion engine in the start-stop mode. The control slide is accordingly moved when stopped in a position in which overheating or unwanted cooling can be prevented by the slide when stopping according to the temperature either closed or opened.

Eine gleichartige Regelung erfolgt vorzugsweise auch in einem Segelbetrieb des Fahrzeugs, in dem der Verbrennungsmotor abgeschaltet wird und entsprechend keine Verbrennungswärme erzeugt. Auch in diesem Zustand kann entsprechend ein unerwünschtes Abkühlen oder Aufheizen in Abhängigkeit der Betriebstemperatur verhindert werden.A similar control is preferably also in a sailing operation of the vehicle in which the engine is switched off and generates no heat of combustion accordingly. In this state as well, undesirable cooling or heating depending on the operating temperature can be prevented.

Des Weiteren ist es vorteilhaft, wenn das Öffnen des Ringspaltes durch eine fortschreitende Druckerhöhung im zweiten Druckraum erfolgt. Diese fortschreitende Druckerhöhung führt zu einem langsamen und kontinuierlichen Öffnen des Regelschiebers, wodurch ein plötzlicher Kaltwasserschwall verhindert wird, der zu einer sprunghaften Abkühlung des Kurbelgehäuses führen könnte.Furthermore, it is advantageous if the opening of the annular gap is effected by a progressive pressure increase in the second pressure chamber. This progressive increase in pressure leads to a slow and continuous opening of the control slide, whereby a sudden cold water surge is prevented, which could lead to a sudden cooling of the crankcase.

In einer besonders bevorzugten Ausbildung des erfindungsgemäßen Verfahrens ist der Schwellwert für die Kühlmitteltemperatur in Abhängigkeit der Umgebungstemperatur in einem Kennfeld hinterlegt. Entsprechend kann für kältere Umgebungstemperaturen der Schwellwert höher angesetzt werden, da eine stärkere Abkühlung beim Abstellen des Verbrennungsmotors auch ohne auftretenden Thermosiphoneffekt erfolgt.In a particularly preferred embodiment of the method according to the invention, the threshold value for the coolant temperature is stored as a function of the ambient temperature in a characteristic map. Accordingly, the threshold value can be set higher for colder ambient temperatures, since a stronger cooling occurs when the internal combustion engine is switched off even without the thermosiphon effect occurring.

Besonders einfach erfolgt die angestrebte Regelung, wenn je nach Stellung eines 3/2-Wege-Elektromagnetventils einer der Druckräume mit unter Druck stehendem Kühlmittel beaufschlagt wird und das 3/2-Wege-Elektromagnetventil beim Abschalten des Verbrennungsmotors angesteuert wird, um den Regelschieber in die geforderte Position zu verfahren. Somit kann durch ein kurzes Signal beim Abstellen der Regelschieber schnell in die gewünschte Position verfahren werden.The desired regulation is particularly simple if, depending on the position of a 3/2-way solenoid valve, one of the pressure chambers is pressurized with pressurized coolant and the 3/2-way solenoid valve is activated when the internal combustion engine is switched off, in order to control the control slide to move to the required position. Thus, a short signal when stopping the control slide can be quickly moved to the desired position.

Es wird somit ein Verfahren zur Regelung einer mechanisch regelbaren Kühlmittelpumpe für eine Verbrennungskraftmaschine geschaffen, bei dem bereits beim Abstellen des Motors für einen optimalen Neustart eine Voreinstellung des Regelschiebers vorgenommen wird, durch den einerseits ein Überhitzen verhindert wird, indem ein ausreichender Kühlmittelstrom sichergestellt wird und andererseits ein zu schnelles Abkühlen des Verbrennungsmotors verhindert wird. Zusätzlich befindet sich der Regelschieber beim Start in der dann optimalen Position, um Warmlaufphasen zu verkürzen.Thus, a method is provided for controlling a mechanically controllable coolant pump for an internal combustion engine, in which a pre-adjustment of the control slide is already made when stopping the engine for optimal restart, on the one hand overheating is prevented by a sufficient coolant flow is ensured and on the other hand too fast cooling of the engine is prevented. In addition, the control slide is at start in the then optimal position to shorten warm-up phases.

Das erfindungsgemäße Verfahren wird anhand einer hierfür geeigneten in den Figuren dargestellten Kühlmittelpumpe für einen Verbrennungsmotor nachfolgend beschrieben.The method according to the invention is described below on the basis of a coolant pump for an internal combustion engine which is suitable for this purpose in the figures.

Figur 1 zeigt eine Seitenansicht einer erfindungsgemäßen Kühlmittelpumpe in geschnittener Darstellung. FIG. 1 shows a side view of a coolant pump according to the invention in a sectional view.

Die dargestellte Kühlmittelpumpe besteht aus einem Außengehäuse 10, in dem ein spiralförmiger Förderkanal 12 ausgebildet ist, in den über einen ebenfalls im Außengehäuse 10 ausgebildeten axialen Pumpeneinlass 14 ein Kühlmittel angesaugt wird, welcher über den Förderkanal 12 zu einem im Außengehäuse 10 ausgebildeten tangentialen Pumpenauslass 16 und in einen Kühlkreislauf der Verbrennungskraftmaschine gefördert wird.The illustrated coolant pump consists of an outer housing 10, in which a spiral conveying channel 12 is formed, into which a coolant is sucked in via an axial pump inlet 14 likewise formed in the outer housing 10, which coolant flows via the delivery channel 12 to a tangential pump outlet 16 and formed in the outer housing 10 is conveyed into a cooling circuit of the internal combustion engine.

Hierzu ist radial innerhalb des Förderkanals 12 auf einer Antriebswelle 18 ein Kühlmittelpumpenlaufrad 20 befestigt, welches als Radialpumpenrad ausgebildet ist, durch dessen Drehung die Förderung des Kühlmittels im Förderkanal 12 erfolgt. An der zum Pumpeneinlass 14 entgegengesetzten axialen Seite des Kühlmittelpumpenlaufrades 20 ist ein Regelpumpenlaufrad 22 ausgebildet, welches entsprechend mit dem Kühlmittelpumpenlaufrad 20 gedreht wird. Dieses Regelpumpenlaufrad 22 weist Schaufeln 24 auf, die axial gegenüberliegend zu einem als Seitenkanal ausgebildeten Strömungskanal 26 angeordnet sind, der in einem ersten inneren Gehäuseteil 28 ausgebildet ist. In diesem ersten Gehäuseteil 28 sind ein nicht sichtbarer Einlass und ein Auslass 30 ausgebildet, so dass das Regelpumpenlaufrad 22 mit dem Strömungskanal 26 eine Regelpumpe 32 bildet, über welche der Druck des Kühlmittels vom Einlass zum Auslass 30 erhöht wird.For this purpose, a coolant pump impeller 20 is fixed radially inside the conveying channel 12 on a drive shaft 18, which is designed as a Radialpumpenrad, by the rotation of the promotion of the coolant takes place in the conveying channel 12. At the pump inlet 14 opposite axial side of the coolant pump impeller 20, a control pump impeller 22 is formed, which is rotated in accordance with the coolant pump impeller 20. This control pump impeller 22 has blades 24, which are arranged axially opposite to a flow channel 26 designed as a side channel, which is formed in a first inner housing part 28. In this first housing part 28, a non-visible inlet and an outlet 30 are formed, so that the control pump impeller 22 forms a control pump 32 with the flow channel 26, via which the pressure of the coolant from the inlet to the outlet 30 is increased.

Der Antrieb des Kühlmittelpumpenlaufrades 20 und des Regelpumpenlaufrades 22 erfolgt über einen Riemen 34, der in ein Riemenrad 36 greift, welches am zum Kühlmittelpumpenlaufrad 20 entgegengesetzten axialen Ende der Antriebswelle 18 befestigt ist. Ein Antrieb über einen Kettentrieb wäre ebenfalls möglich. Das Riemenrad 36 ist über ein zweireihiges Kugellager 38 auf einem zweiten Gehäuseteil 40 gelagert. Das zweite Gehäuseteil 40 weist eine innere axiale Durchgangsöffnung 42 auf, in die ein ringförmiger Vorsprung 44 des ersten Gehäuseteils 28 ragt, über den das erste Gehäuseteil 28 am zweiten Gehäuseteil 40 befestigt ist. Das zweite Gehäuseteil 40 ist unter Zwischenlage einer Dichtung 46 am Außengehäuse 10 befestigt. Hierzu weist das Außengehäuse 10 an seinem zum Pumpeneinlass 14 entgegengesetzten axialen Ende eine Aufnahmeöffnung 48 auf, in die ein ringförmiger Vorsprung 50 des zweiten Gehäuseteils 40 ragt.The drive of the coolant pump impeller 20 and the control pump impeller 22 via a belt 34 which engages in a pulley 36 which is secured to the coolant pump impeller 20 opposite axial end of the drive shaft 18. A drive via a chain drive would also be possible. The pulley 36 is mounted on a second housing part 40 via a double-row ball bearing 38. The second housing part 40 has an inner axial passage opening 42 into which an annular projection 44 of the first housing part 28 projects, via which the first housing part 28 is fastened to the second housing part 40. The second housing part 40 is under Interposed layer of a seal 46 attached to the outer housing 10. For this purpose, the outer housing 10 at its pump inlet 14 opposite axial end a receiving opening 48 into which an annular projection 50 of the second housing part 40 projects.

Der ringförmige Vorsprung 50 dient gleichzeitig als rückwärtiger Anschlag 52 für einen Regelschieber 54, dessen zylindrische Umfangswand 56 derart über das Kühlmittelpumpenlaufrad 20 geschoben werden kann, dass ein freier Querschnitt eines Ringspalts 58 zwischen einem Austritt 60 des Kühlmittelpumpenlaufrades 20 und dem Förderkanal 12 geregelt wird. Entsprechend der Stellung dieses Regelschiebers 54 wird somit der durch den Kühlmittelkreislauf geförderte Kühlmittelstrom geregelt.The annular projection 50 also serves as a rear stop 52 for a control slide 54, the cylindrical peripheral wall 56 can be pushed over the coolant pump impeller 20 so that a free cross section of an annular gap 58 between an outlet 60 of the coolant pump impeller 20 and the delivery channel 12 is controlled. In accordance with the position of this control slide 54, the coolant flow conveyed through the coolant circuit is thus regulated.

Der Regelschieber 54 weist neben der Umfangswand 56 einen Boden 62 mit einer inneren Öffnung 64 auf, von dessen Außenumfang aus sich die Umfangswand 56 axial durch einen ringförmigen Spalt 66 zwischen dem ersten Gehäuseteil 28 und dem Außengehäuse 10 in Richtung des sich axial anschließenden Ringspaltes 58 erstreckt. Am inneren Umfang und am äußeren Umfang des Bodens 62 ist jeweils in einer Radialnut ein Kolbenring 68 angeordnet, über die der Regelschieber 54 im radial inneren Bereich auf dem ersten Gehäuseteil 28 und im radial äußeren Bereich im ringförmigen Vorsprung 50 des zweiten Gehäuseteils 40 gleitend gelagert ist.The control slide 54 has, in addition to the peripheral wall 56, a bottom 62 with an inner opening 64, from the outer periphery of which the circumferential wall 56 extends axially through an annular gap 66 between the first housing part 28 and the outer housing 10 in the direction of the axially adjoining annular gap 58 , On the inner periphery and on the outer circumference of the bottom 62, a piston ring 68 is arranged in each case in a radial groove, via which the control slide 54 is slidably mounted in the radially inner region on the first housing part 28 and in the radially outer region in the annular projection 50 of the second housing part 40 ,

An der vom Kühlmittelpumpenlaufrad 20 abgewandten Seite des Regelschiebers 54 befindet sich ein erster Druckraum 70, der axial durch das zweite Gehäuseteil 40 und den Boden 62 des Regelschiebers 54 und radial nach außen durch das Außengehäuse 10 beziehungsweise den ringförmigen Vorsprung 50 des zweiten Gehäuseteils 40 und nach radial innen durch das erste Gehäuseteil 28 begrenzt wird. An der zum Kühlmittelpumpenlaufrad 20 gewandten Seite des Bodens 62 wird ein zweiter Druckraum 72 gebildet, der axial durch den Boden 62 und das erste Gehäuseteil 28, nach radial außen durch die Umfangswand 56 des Regelschiebers 54 und nach radial innen durch das erste Gehäuseteil 28 begrenzt wird. Je nach am Boden 62 des Regelschiebers 54 in den beiden Druckräumen 70, 72 anliegender Druckdifferenz wird die Umfangswand 56 des Regelschiebers 54 entsprechend in den Ringspalt 58 hinein- oder aus dem Ringspalt 58 herausgeschoben.At the side facing away from the coolant pump impeller 20 side of the control slide 54 is a first pressure chamber 70 axially through the second housing part 40 and the bottom 62 of the control slide 54 and radially outwardly through the outer housing 10 and the annular projection 50 of the second housing part 40 and after is limited radially inwardly by the first housing part 28. On the side facing the coolant pump impeller 20 side of the bottom 62, a second pressure chamber 72 is formed, which extends axially through the bottom 62 and the first housing part 28, radially outwardly through the peripheral wall 56 of Control slide 54 and radially inwardly limited by the first housing part 28. Depending on the bottom 62 of the control slide 54 in the two pressure chambers 70, 72 adjacent pressure difference, the peripheral wall 56 of the control slide 54 in accordance with the annular gap 58 hinein- or pushed out of the annular gap 58.

Die hierzu notwendige Druckdifferenz wird durch die Regelpumpe 32 erzeugt und mittels eines Ventils 74, welches als 3/2-Wege-Magnetventil ausgebildet ist, dem jeweiligen Druckraum 70, 72 zugeführt. Hierzu ist im zweiten Gehäuseteil 40 eine Aufnahmeöffnung 76 für das Ventil 74 ausgebildet, über welches je nach Position seines Schließkörpers 78 ein Durchströmungsquerschnitt 80 eines Druckkanals 82 geregelt wird. Dieser Druckkanal 82 erstreckt sich vom Auslass 30 des Strömungskanals 26 der Regelpumpe 32 bis zum ersten Druckraum 70. Der zweite Druckraum 72 ist über einen Verbindungskanal, welcher im ersten Gehäuseteil 28 ausgebildet ist, mit dem Strömungskanal 26 verbunden, wobei dieser Verbindungskanal durch eine Bohrung gebildet ist, die sich von einem Bereich des Einlasses aus dem Strömungskanal 26 direkt in den zweiten Druckraum erstreckt. Ein dritter, nicht dargestellter Strömungsanschluss des Regelventils führt zur Saugseite der Kühlmittelpumpe.The required pressure difference is generated by the control pump 32 and by means of a valve 74, which is designed as a 3/2-way solenoid valve, the respective pressure chamber 70, 72, respectively. For this purpose, a receiving opening 76 for the valve 74 is formed in the second housing part 40, via which, depending on the position of its closing body 78, a flow cross-section 80 of a pressure channel 82 is controlled. This pressure channel 82 extends from the outlet 30 of the flow channel 26 of the control pump 32 to the first pressure chamber 70. The second pressure chamber 72 is connected via a connecting channel, which is formed in the first housing part 28, with the flow channel 26, said connecting channel formed by a bore is that extends from a region of the inlet from the flow channel 26 directly into the second pressure chamber. A third, not shown, flow connection of the control valve leads to the suction side of the coolant pump.

Soll die Kühlmittelpumpe im Betrieb eine maximale Kühlmittelmenge fördern, wird der Ringspalt 58 am Austritt 60 des Kühlmittelpumpenlaufrades 20 vollständig freigegeben, indem das Magnetventil 74 nicht bestromt wird, wodurch der Schließkörper 78 aufgrund einer Federkraft in seine den Durchströmungsquerschnitt 80 des Druckkanals 82 verschließende Stellung verschoben wird. Dies hat zur Folge, dass im ersten Druckraum 70 kein Druck durch das Kühlmittel aufgebaut wird, sondern das im Druckraum 70 vorhandene Kühlmittel über den nicht dargestellten anderen Strömungsanschluss des Magnetventils 74, der in diesem Zustand freigegeben ist, zum Pumpeneinlass 14 der Kühlmittelpumpe abströmen kann. Stattdessen fördert in diesem Zustand die Regelpumpe 32 gegen den geschlossenen Durchströmungsquerschnitt 80, wodurch sich im gesamten Strömungskanal 26 ein erhöhter Druck aufbaut, der auch im Bereich des Einlasses der Regelpumpe 32 wirkt und sich entsprechend über den Verbindungskanal auch im zweiten Druckraum 72 aufbaut. Dieser erhöhte Druck im zweiten Druckraum 72 hat zur Folge, dass am Boden 62 des Regelschiebers 54 eine Druckdifferenz entsteht, die dazu führt, dass der Regelschieber 54 in seine den Ringspalt 58 freigebende Position verschoben wird und somit eine Maximalförderung der Kühlmittelpumpe sichergestellt wird.If the coolant pump to promote a maximum amount of coolant during operation, the annular gap 58 at the outlet 60 of the coolant pump impeller 20 is fully released by the solenoid valve 74 is not energized, whereby the closing body 78 is moved due to a spring force in its the flow cross-section 80 of the pressure channel 82 occlusive position , As a result, no pressure is built up by the coolant in the first pressure chamber 70, but the coolant present in the pressure chamber 70 can flow to the pump inlet 14 of the coolant pump via the not shown other flow connection of the solenoid valve 74, which is released in this state. Instead promotes in this state, the control pump 32 against the closed flow cross-section 80, which builds up an increased pressure in the entire flow channel 26, which also acts in the region of the inlet of the control pump 32 and correspondingly builds on the connection channel in the second pressure chamber 72. This increased pressure in the second pressure chamber 72 has the result that at the bottom 62 of the control slide 54, a pressure difference arises, which causes the control slide 54 is moved to its annular gap 58 releasing position and thus a maximum delivery of the coolant pump is ensured.

Wird ein reduzierter Kühlmittelstrom zum Kühlkreislauf von der Motorsteuerung gefordert, wie dies beispielsweise während des Warmlaufs des Verbrennungsmotors nach dem Kaltstart der Fall ist, wird das Magnetventil 74 bestromt, wodurch der Schließkörper 78 den Durchströmungsquerschnitt 80 des Druckkanals 82 freigibt. Entsprechend wird der am Auslass der Regelpumpe 32 entstehende Druck auch im Druckkanal 82 und im ersten Druckraum 70 erzeugt, während gleichzeitig der Druck im zweiten Druckraum 72 sinkt, da im Bereich des Einlasses durch das Ansaugen des Kühlmittels ein verringerter Druck entsteht. Dabei wird zunächst auch das im zweiten Druckraum 72 vorhandene Kühlmittel abgesaugt. In diesem Zustand liegt entsprechend erneut eine Druckdifferenz am Boden 62 des Regelschiebers 54 an, die dazu führt, dass der Regelschieber 54 in den Ringspalt 58 verschoben wird und somit der Kühlmittelstrom im Kühlkreislauf unterbrochen wird.If a reduced coolant flow to the cooling circuit is required by the engine control, as is the case, for example, during the warm-up of the internal combustion engine after the cold start, the solenoid valve 74 is energized, whereby the closing body 78 releases the flow cross-section 80 of the pressure channel 82. Accordingly, the pressure generated at the outlet of the control pump 32 is also generated in the pressure channel 82 and in the first pressure chamber 70, while at the same time the pressure in the second pressure chamber 72 decreases, since in the region of the inlet by the suction of the coolant, a reduced pressure. In this case, the coolant present in the second pressure chamber 72 is initially aspirated. In this state, again corresponding to a pressure difference at the bottom 62 of the control slide 54, which causes the control slide 54 is moved into the annular gap 58 and thus the flow of coolant in the cooling circuit is interrupted.

Wird ein Magnetventil 74, welches als Proportionalventil oder getaktetes Ventil mit variablem Tastverhältnis ausgeführt ist, verwendet, ist es auch möglich, das Ventil 74 in Zwischenstellungen zu fahren, wodurch für jede Position des Regelschiebers 54 ein Kräftegleichgewicht erzielbar ist, so dass eine vollständige Regelung des Durchströmungsquerschnitts des Ringspaltes 58 ermöglicht wird.If a solenoid valve 74, which is designed as a proportional valve or clocked valve with a variable duty cycle, used, it is also possible to drive the valve 74 in intermediate positions, whereby for each position of the control slide 54, a balance of forces can be achieved, so that a complete control of Throughflow cross section of the annular gap 58 is made possible.

Zur Verstellung des Regelschiebers 54 wird entsprechend keine Federkraft verwendet. Stattdessen behält der Regelschieber 54 dieser Kühlmittelpumpe beim Abstellen des Verbrennungsmotors und dem daraus folgenden Stillstand beider Pumpenlaufräder 20, 22 jeweils die Position bei, die er zum Zeitpunkt des Abstellens aufweist, da lediglich durch Leckagen ein Druck in einem Druckraum abgebaut werden kann, was jedoch nicht zu einer Verstellung des Regelschiebers 54 führt, da dann in beiden Druckräumen im statischen Zustand ein Druckgleichgewicht herrscht, jedoch für eine Verstellung Reibungskräfte zu überwinden wären.To adjust the control slide 54, no spring force is used accordingly. Instead, the control slide 54 of this coolant pump when stopping the engine and the consequent stoppage of both pump impellers 20, 22 respectively at the position that it has at the time of shutdown, since only a pressure in a pressure chamber can be reduced by leaks, but not leads to an adjustment of the control slide 54, since then there is a pressure equilibrium in both pressure chambers in the static state, but friction forces would have to be overcome for an adjustment.

Dies wird erfindungsgemäß genutzt, um die Kühlmittelpumpe derart zu regeln, dass beim Abstellen des Verbrennungsmotors das Magnetventil 74 derart geschaltet wird, dass der Regelschieber 54 jeweils eine für einen folgenden Startvorgang optimierte Ausgangsstellung aufweist. Dies erfolgt insbesondere in Abhängigkeit der aktuellen Kühlmitteltemperatur im Vergleich zu einem definierten Schwellwert, der beispielsweise der üblichen Betriebstemperatur der Verbrennungskraftmaschine von beispielsweise etwa 95°C entspricht.This is used according to the invention to regulate the coolant pump in such a way that, when the internal combustion engine is switched off, the solenoid valve 74 is switched in such a way that the control slide 54 in each case has an initial position optimized for a following starting process. This is done in particular as a function of the current coolant temperature in comparison to a defined threshold, which corresponds for example to the usual operating temperature of the internal combustion engine, for example, about 95 ° C.

Wird nun beispielsweise die Zündung des Verbrennungsmotors abgestellt und die Temperatur des Kühlmittels beträgt 96°C, liegt also über dem Schwellwert, wird das Magnetventil 74 nicht bestromt, wodurch der Druck im zweiten Druckraum 72 steigt und der Regelschieber 54 in seine den Ringspalt 58 freigebende Stellung verschoben wird. Dies hat zur Folge, dass bei abgeschaltetem Verbrennungsmotor das Kühlmittel aufgrund des Thermosiphoneffektes weiterhin zirkuliert und so weitere Wärme des noch heißen Verbrennungsmotor aufnimmt. Für dieses Abstellen kann jedoch auch der umgekehrte Weg beschritten werden und der Regelschieber 54 durch Bestromung des Magnetventils 74 in seine den Ringspalt 58 verschließende Position verfahren werden. Dies hat zur Folge, dass bei längerer Standzeit eine Abkühlung einsetzt, jedoch die Wärmemenge etwas länger gespeichert wird. Bei einem folgenden Start wäre der Regelschieber 54 in seiner verschließenden Position, so dass eine schnelle erneute Aufheizung des Kühlmittels zur Verkürzung der Warmlaufphase erfolgen würde. Ob der Regelschieber 54 beim Abstellen der Zündung in seine offene oder geschlossene Position verfahren wird, kann beispielsweise auch in Abhängigkeit der Außentemperatur entschieden werden. Bei besonders hohen Temperaturen würde der Regelschieber 54 dann eher in den offenen Zustand verfahren, um eine ausreichende Wärmeabfuhr sicher zu stellen und so ein Überhitzen des Motors zu verhindern.If, for example, the ignition of the internal combustion engine is turned off and the temperature of the coolant is 96 ° C., ie above the threshold value, the solenoid valve 74 is not energized, whereby the pressure in the second pressure chamber 72 increases and the control slide 54 in its annular gap 58 releasing position is moved. As a result, with the internal combustion engine switched off, the coolant continues to circulate due to the thermosiphon effect and thus absorbs further heat from the still hot combustion engine. However, the reverse path can also be taken for this shutdown and the control slide 54 are moved by energizing the solenoid valve 74 in its closing the annular gap 58 position. This has the consequence that a longer life, a cooling begins, but the amount of heat is stored a little longer. At a following start would be the Regulator valve 54 in its occluding position, so that a rapid re-heating of the coolant to shorten the warm-up phase would take place. Whether the control slide 54 is moved when switching off the ignition in its open or closed position, for example, depending on the outside temperature can be decided. At particularly high temperatures, the control slide 54 would then rather moved into the open state, to ensure sufficient heat dissipation and thus to prevent overheating of the engine.

Eine entsprechende Regelung kann auch für Fahrzeuge mit einer Start-Stopp-Automatik erfolgen. Wird der Motor im Start-Stopp-Betrieb abgestellt, sollte der Regelschieber 54 in Abhängigkeit der momentanen Kühlmitteltemperatur in den den Ringspalt 58 öffnenden Zustand verfahren werden, wenn die Betriebstemperatur erreicht und somit der Schwellwert überschritten ist, da nur von kurzen Standzeiten auszugehen ist, in denen keine große Abkühlung zu erwarten ist, jedoch eine Überhitzung des Kühlmittels durch den warmen Motor erfolgen könnte. Entsprechend erfolgt im abgestellten Zustand eine Zirkulation durch den Thermosiphoneffekt. Bei Start des Verbrennungsmotors befindet sich der Regelschieber dann in dieser Position, so dass ohne Zeitverzögerung wieder eine maximale Kühlmittelförderung stattfinden kann. Sollte die Betriebstemperatur noch nicht erreicht sein, wird der Regelschieber 54 beim Abschalten im den Ringspalt 58 verschließenden Zustand belassen oder in diesen bewegt. Dadurch wird eine Zirkulation des Kühlmittels ausgeschlossen und der Motor kann seine Wärme an das stehende Kühlmittel abgeben. Beim erneuten Start erfolgt ein weiteres Aufheizen des stehenden Kühlmittels, so dass die Warmlaufphase verkürzt wird. Anschließend wird der Regelschieber 54 lediglich langsam geöffnet, um zu verhindern dass ein kalter Kühlmittelschwall aus der Pumpe in das Kurbelgehäuse strömt.A corresponding regulation can also be made for vehicles with an automatic start-stop system. If the engine is turned off in the start-stop mode, the control slide 54 should be moved depending on the current coolant temperature in the opening state of the annular gap 58, when the operating temperature is reached and thus the threshold is exceeded, since only short life is to be assumed in where no great cooling is to be expected, however, an overheating of the coolant could be done by the warm engine. Accordingly, in the parked state, circulation takes place through the thermosiphon effect. When starting the engine, the control slide is then in this position, so that again can take place without time delay again maximum coolant delivery. If the operating temperature has not yet been reached, the control slide 54 is left when switching off in the annular gap 58 occlusive state or moved into this. This precludes circulation of the coolant and allows the engine to deliver its heat to the standing coolant. When restarting a further heating of the stationary coolant takes place, so that the warm-up phase is shortened. Subsequently, the control slide 54 is only slowly opened to prevent a cold coolant surge from the pump flows into the crankcase.

Eine entsprechende Regelung sollte auch während des Segelbetriebes des Kraftfahrzeugs erfolgen, in dem der Verbrennungsmotor vom Antriebsstrang abgekuppelt und ausgeschaltet wird. Nach dem Abschalten des Verbrennungsmotors kann anschließend die Bestromung des Ventils 74 beendet werden, ohne dass der Regelschieber 54 bei abgeschaltetem Motor verschoben wird. Nach dem erneuten Motorstart erfolgt die bekannte bedarfsabhängige Regelung des Regelschiebers. Diese folgende Regelung kann entweder über einen geschlossenen Regelkreis mit einer Lagerückmeldung des Regelschiebers erfolgen oder ohne Sensorik durchgeführt werden.A corresponding regulation should also take place during the sailing operation of the motor vehicle, in which the internal combustion engine is disconnected from the drive train and switched off. After switching off the internal combustion engine, the energization of the valve 74 can then be terminated without the control slide 54 being displaced when the engine is switched off. After re-starting the engine, the known demand-dependent control of the control slide takes place. This following control can be done either via a closed loop with a bearing feedback of the control slide or performed without sensors.

Ein derartiges Verfahren ermöglicht einerseits eine Regelung des Kühlmittelstroms bei abgestelltem Fahrzeug innerhalb der physikalisch vorhandenen Grenzen als auch eine optimale Stellung des Regelschiebers und damit des Kühlmittelstroms unmittelbar beim Startvorgang des Fahrzeugs, wodurch die Kaltlaufphase verkürzt werden kann. Insgesamt können die vorhandenen Wärmemengen besser genutzt werden und dennoch eine Überhitzung in allen Betriebszuständen sicher vermieden werden.Such a method allows on the one hand a control of the coolant flow with the vehicle parked within the physically existing limits and an optimal position of the control slide and thus the coolant flow immediately during the starting process of the vehicle, whereby the cold running phase can be shortened. Overall, the existing amounts of heat can be used better and yet overheating safely avoided in all operating conditions.

Es sollte deutlich sein, dass der Schutzbereich des Hauptanspruchs nicht auf das beschriebene Ausführungsbeispiel begrenzt ist. Insbesondere können andere Kühlmittelpumpen verwendet werden, wobei lediglich wichtig ist, dass der Regelschieber nicht durch äußere Kräfte nach dem Abschalten verschoben wird. Auch können verschiedene Schaltpunkte zur Regelung gewählt werden oder Zwischenstellungen des Schiebers angefahren werden, wenn dies sinnvoll ist.It should be clear that the scope of the main claim is not limited to the embodiment described. In particular, other coolant pumps can be used, it being only important that the control slide is not displaced by external forces after switching off. Also, different switching points can be selected for control or intermediate positions of the slide can be approached, if that makes sense.

Claims (11)

  1. A method for controlling a mechanically controllable coolant pump for an internal combustion engine, where a coolant is delivered via a coolant pump impeller (20) into a delivery duct (12) surrounding said coolant pump impeller (20) and to a pump outlet (16),
    wherein the delivery is dependent on the position of an adjustable control slide (54) via which a throughflow cross-section of an annular gap (58) between an outlet (60) of said coolant pump impeller (20) and said surrounding flow duct (12) is controlled,
    and wherein for reducing the coolant volume flow delivered to said pump outlet (16) by decreasing the throughflow cross-section a first pressure chamber (70) on a first axial side of said control slide (54) is filled with a pressurized coolant,
    characterized in that
    for increasing the coolant volume flow delivered to said pump outlet (16) by increasing the throughflow cross-section a second pressure space (72) on a side of said control slide (54) axially opposite to the first side is filled with a pressurized coolant and during switch-off of the internal combustion engine said control slide (54) is moved into a defined position, depending on the coolant temperature, in which said control slide (54) remains until the engine is started.
  2. The method for controlling a mechanically controllable coolant pump for an internal combustion engine according to claim 1,
    characterized in that
    the control slide (54) is moved into a position for closing the annular gap (58) during switch-off of the internal combustion engine when the coolant temperature falls below a defined threshold value.
  3. The method for controlling a mechanically controllable coolant pump for an internal combustion engine according to claim 2,
    characterized in that
    the control slide (54) is moved into a position for fully opening the annular gap (58) during switch-off of the internal combustion engine when the coolant temperature corresponds to the defined threshold value or exceeds the defined threshold value.
  4. The method for controlling a mechanically controllable coolant pump for an internal combustion engine according to any one of claims 2 or 3,
    characterized in that
    the threshold value corresponds to a desired value for the operating temperature of the coolant during operation as defined in the engine control.
  5. The method for controlling a mechanically controllable coolant pump for an internal combustion engine according to any one of the preceding claims,
    characterized in that
    the control during switch-off of the internal combustion engine is performed by cutting off the ignition of said internal combustion engine.
  6. The method for controlling a mechanically controllable coolant pump for an internal combustion engine according to claim 5,
    characterized in that
    during cut-off of the ignition of the internal combustion engine the control slide (54) is moved into a position for closing the annular gap (58).
  7. The method for controlling a mechanically controllable coolant pump for an internal combustion engine according to any one of the preceding claims,
    characterized in that
    the control during switch-off of the internal combustion engine is performed in the start-stop operation.
  8. The method for controlling a mechanically controllable coolant pump for an internal combustion engine according to any one of the preceding claims,
    characterized in that
    the control is performed in a coasting mode of the vehicle.
  9. The method for controlling a mechanically controllable coolant pump for an internal combustion engine according to any one of the preceding claims,
    characterized in that
    opening of the annular gap (58) is effected by a progressive pressure increase in the second pressure chamber (72).
  10. The method for controlling a mechanically controllable coolant pump for an internal combustion engine according to any one of claims 2 to 4,
    characterized in that
    the threshold value for the coolant temperature as a function of the ambient temperature is saved in a characteristic map.
  11. The method for controlling a mechanically controllable coolant pump for an internal combustion engine according to any one of the preceding claims,
    characterized in that
    depending on the position of a 3/2-way electromagnetic valve (74) a pressurized coolant is fed to one of the pressure chambers (70, 72) and the 3/2-way electromagnetic valve (74) is driven during switch-off of the internal combustion engine for moving the control slide (54) into the required position.
EP16787373.6A 2015-11-06 2016-10-19 Method for controlling a mechanically controllable coolant pump for an internal combustion engine Active EP3371464B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102015119092.3A DE102015119092B4 (en) 2015-11-06 2015-11-06 Method for controlling a mechanically controllable coolant pump for an internal combustion engine
PCT/EP2016/075081 WO2017076648A1 (en) 2015-11-06 2016-10-19 Method for controlling a mechanically controllable coolant pump for an internal combustion engine

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EP3371464A1 EP3371464A1 (en) 2018-09-12
EP3371464B1 true EP3371464B1 (en) 2019-11-27

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US (1) US10578006B2 (en)
EP (1) EP3371464B1 (en)
JP (1) JP6584665B2 (en)
CN (1) CN108350888B (en)
DE (1) DE102015119092B4 (en)
WO (1) WO2017076648A1 (en)

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Publication number Publication date
US20180313251A1 (en) 2018-11-01
DE102015119092A1 (en) 2017-05-24
JP2018532942A (en) 2018-11-08
DE102015119092B4 (en) 2019-03-21
CN108350888B (en) 2019-11-01
EP3371464A1 (en) 2018-09-12
US10578006B2 (en) 2020-03-03
JP6584665B2 (en) 2019-10-09
WO2017076648A1 (en) 2017-05-11
CN108350888A (en) 2018-07-31

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