EP3371463B1 - Control arrangement for a mechanically controllable coolant pump of an internal combustion engine - Google Patents

Control arrangement for a mechanically controllable coolant pump of an internal combustion engine Download PDF

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Publication number
EP3371463B1
EP3371463B1 EP16785429.8A EP16785429A EP3371463B1 EP 3371463 B1 EP3371463 B1 EP 3371463B1 EP 16785429 A EP16785429 A EP 16785429A EP 3371463 B1 EP3371463 B1 EP 3371463B1
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EP
European Patent Office
Prior art keywords
control
coolant pump
pump
flow
internal combustion
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EP16785429.8A
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German (de)
French (fr)
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EP3371463A1 (en
Inventor
Stephan Zielberg
Michael-Thomas Benra
Michael Sanders
Stefan Rothgang
Andreas Burger
Sven Nigrin
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Pierburg GmbH
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Pierburg GmbH
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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
    • F04D15/0027—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
    • F01P5/00—Pumping cooling-air or liquid coolants
    • F01P5/10—Pumping liquid coolant; Arrangements of coolant pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D13/00—Pumping installations or systems
    • F04D13/12—Combinations of two or more pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P5/00—Pumping cooling-air or liquid coolants
    • F01P5/10—Pumping liquid coolant; Arrangements of coolant pumps
    • F01P2005/105—Using two or more pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2270/00—Control
    • F05D2270/60—Control system actuates means
    • F05D2270/64—Hydraulic actuators

Definitions

  • the invention relates to a control arrangement for a mechanically controllable coolant pump of an internal combustion engine with an adjustable control slide, via which a flow cross section of an annular gap between an outlet of adeffenpumpenterrorisms and a surrounding conveyor channel is controllable, a control pump, via which a hydraulic pressure can be generated, a first pressure chamber of the A control slide, which is formed on a first axial side of the control slide and a solenoid valve having two valve seats and three flow ports and a closing member which is connected to an armature of the solenoid valve and axially movable, wherein the first flow port is fluidly connected to an outlet of the control pump and the second flow connection is fluidically connected to the first pressure chamber of the control slide.
  • Such control arrangements for 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 should of the engine are shortened. This is done, inter alia, by throttling or completely shutting off the coolant flow during this phase.
  • control slide also takes place in different ways.
  • a hydraulic adjustment of the slide has proven. This is usually done via an annular piston chamber or otherwise executed pressure chamber which is filled with a hydraulic fluid to move when filling the slide on the coolant pump impeller.
  • a return of the control slide is done by opening the pressure chamber to an outlet, which is usually done via a 2/2-way solenoid valve and under the action of a spring, which provides the force to return the slide.
  • control arrangements In order not to have to provide the process of the control slide coolant amount on additional conveyor units, such as additional piston / cylinder units or compress other hydraulic fluids for actuation, control arrangements have become known in which a necessary pressure generating control pump on the drive shaft Coolant pump is arranged, which serves to adjust the slide accordingly.
  • control pumps are designed, for example, as side channel pumps or servo pumps.
  • a control arrangement for a mechanically driven, controllable coolant pump with a control pump, which generates a pressure for displacement of a control slide is known from DE 10 2012 207 387 A1 known.
  • a pressure side of the control 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.
  • the first flow connection of the valve to the pressure chamber the second flow connection to the outlet of the control pump and the third flow connection to the inlet of the control pump.
  • a detailed channel and flow guidance of the control arrangement is not disclosed.
  • the flow guides shown schematically are technically feasible in modern internal combustion engines only with increased effort and space requirements.
  • a quick emptying of the piston chamber is not possible because the emptying takes place to the inlet of the control pump, which builds up a pressure in the entire channel, which acts as a back pressure in the piston chamber.
  • a provision of the slide in its maximum flow rate of the coolant pump locking position should possible without use a force acting on the control slide compression spring can be done. Furthermore, a variable control of the coolant flow should be possible if possible.
  • the third flow port is fluidly connected to an inlet of the coolant pump, wherein the first valve seat between the first flow port and the second flow port is formed and the second valve seat is formed between the second flow port and the third flow port, either a connection between the Pressure chamber and the inlet of the coolant pump are made, whereby the coolant there existing quickly sucked off and thus the pressure in the pressure chamber can be degraded quickly or a connection from the outlet of the control pump to the pressure chamber are made, whereby a pressurization of the pressure chamber and thus of the control slide , Thus, a short-term adjustment of the control slide is made possible by switching the solenoid valve.
  • the solenoid valve preferably has a flow housing in which the closing member is axially movable between the two valve seats and an electromagnetic actuator with a core, flux guide elements, a winding arranged on a coil carrier and the axially movable armature.
  • the closing member only has to travel short distances, whereby the switching times are reduced.
  • At least the flow housing of the solenoid valve is arranged in a receiving opening of a housing part of the coolant pump.
  • the solenoid valve is arranged in close proximity to the control pump, whereby the length of the lines is reduced, which also leads to a shortening of the switching times of the control arrangement.
  • little space is needed and the installation is simplified because the entire control arrangement can be pre-assembled with the coolant pump and inserted into the outer housing.
  • a first channel is formed in the housing part, via which the first pressure chamber is connected to the second flow connection. Additional lines are omitted. Instead, extremely short connections are created for faster switching times.
  • a second channel is formed, which is on the one hand connected to the first flow port of the solenoid valve and on the other hand continues in the control pump housing to the outlet of the control pump.
  • a third channel is preferably formed in the housing part, which is connected on the one hand to the third flow port of the solenoid valve and on the other hand extends into a radially inner passage opening of the housing part, which continues in the interior of the control pump housing and projects through the drive shaft of the coolant pump, wherein in the coolant pump impeller, an axial bore is formed, which leads to the inlet of the coolant pump.
  • a channel is formed in the region of an inlet of the control pump, via which a second pressure chamber is fluidically connected to the flow channel of the control pump, so that the coolant pump is constructed without additional, a continuous force applying means, such as compression springs and the like. This reduces the required control forces, which again switching the control arrangement with very short reaction times is possible.
  • the closing member of the solenoid valve is arranged on a valve rod, wherein a closing surface at a first axial end of the closing member is associated with the first valve seat and a closing surface is associated with the second valve seat at the opposite axial end.
  • the axial bearing of the closing member on the respective valve seat leads to a dense, almost leak-free closure of the respective flow cross-section. For this purpose, only a double-loaded locking member is required, whereby the structure of the solenoid valve is also facilitated.
  • the solenoid valve is preferably designed as a proportional valve. This allows a continuous control of the valve opening, so that the control slide is movable in intermediate positions and thus the coolant flow can be completely controlled. These valves had a long service life, since the high-frequency impingement of the valve body on the valve seat is eliminated.
  • the solenoid valve is variable clocked controlled.
  • Such a controlled servo valve is more expensive to manufacture, but allows an even more accurate Rules of the desired opening cross sections, so that even more accurate control of the position of the control slide is possible.
  • the illustrated coolant pump 11 consists of an outer housing 10, in which a spiral conveying channel 12 is formed, in which a coolant is sucked in via an axial inlet 14 likewise formed in the outer housing 10, which coolant flows via the delivery channel 12 to a tangential pump outlet 16 formed in the outer housing 10 and 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 serves as Radialpumpenrad is formed by the rotation of the promotion of the coolant takes place in the conveying channel 12.
  • the drive of the coolant pump impeller 20 via a belt 22 which engages in a pulley 24 which is secured to the coolant pump impeller 20 opposite axial end of the drive shaft 18.
  • the pulley 24 is supported by a double-row ball bearing 26, which is pressed onto a stationary housing part 28, which is fastened to the outer housing 10 with the interposition of a seal 30.
  • the housing part 28 has an annular projection 32, which is fitted into a corresponding receptacle of the outer housing 10.
  • a control arrangement 34 of the coolant pump 11 is formed on the axial side of the coolant pump impeller 20 opposite the inlet 14.
  • This consists of a control pump 36 with a control pump impeller 38, which is integrally formed with the coolant pump impeller 20 and is rotated in accordance with the coolant pump impeller 20.
  • This control pump impeller 38 has blades 40 which are arranged axially opposite to a flow channel 42 designed as a side channel, which is formed in a control pump housing 44.
  • a not visible in this illustration inlet and an outlet 46 are formed, through which the coolant can flow or can flow at elevated pressure.
  • the control pump housing 44 has, just like the housing part 28, an inner axial through opening 48, through which the drive shaft 18 extends with the interposition of a seal 50 in the region of the housing part 28 and is fastened to the housing part 28.
  • a ring-shaped projection 52 facing the housing part 28 is formed on the control pump housing 44, which protrudes into a corresponding receiving opening 49 of the housing part 28, whereby a prefixing takes place.
  • the control pump housing 44 via screws 54, the extend through the control pump housing 44 into corresponding threaded bores of the housing part 28, attached.
  • the movement of the control slide 56 is limited on the one hand by the end of the annular gap 60, on the other hand by the projection 32, against the axial end of a shoulder 64 of the peripheral wall 58 in the completely releasing the annular gap 60 position of the control slide 56 is applied.
  • the control slide 56 has, in addition to the peripheral wall 58, a bottom 66, from the outer periphery of which the circumferential wall 58 extends axially between the control pump housing 44 and the outer housing 10 in the direction of the axially adjoining annular gap 60.
  • a bottom 66 In the radially inner region of the bottom 66 has an opening 68 which is delimited by a hollow cylindrical portion 70, via which the control slide 56 is mounted on the control pump housing 44.
  • a radial groove is formed, in each of which a piston ring 71 is arranged, via which the two axially opposite sides of the control slide 56 are sealed to one another.
  • a first pressure chamber 72 axially through the housing part 28 and the bottom 66 of the control slide 56 and radially outwardly through the outer housing 10 and the annular projection 32 of the housing part 28 and radially inward is limited by the control pump housing 44.
  • a second pressure chamber 74 is formed axially through the bottom 66 and the Rule pump housing 44 is limited radially outward by the peripheral wall 58 of the control slide 56 and radially inwardly by the control pump housing 44.
  • the peripheral wall 58 of the control slide 56 in accordance with the annular gap 60 in or out of the annular gap 60 pushed out.
  • the required pressure difference is generated by the control pump 36, wherein the corresponding pressure in response to the position of a closing member 76 of a 3/2-way solenoid valve 78 to the respective pressure chamber 72, 74 is supplied.
  • a receiving opening 80 for the solenoid valve 78 is formed in the housing part 28, in which a flow housing 82 of the solenoid valve 78 is received.
  • the solenoid valve 78 is in the FIG. 3 shown. It consists of an electromagnetic actuator 84 and a valve unit 86.
  • the actuator 84 has a winding 90 arranged on a coil support 88, in the interior of which there is a core 92 and which is surrounded axially and radially by flux-conducting elements 94 of the electromagnetic circuit.
  • an axially movable armature 96 is pulled in the direction of the core 92.
  • This movement takes place counter to the force of a spring 98, which is arranged between the core 92 and the armature 96 in a recess 100 on the core 92 and surrounds a non-magnetizable, core 92 fixed pin 102, which serves as a stop for the armature 96, so that it does not abut the core 92 in its shifted position relative to the core 92, since this would lead to undesired adhesive forces.
  • a spring 98 which is arranged between the core 92 and the armature 96 in a recess 100 on the core 92 and surrounds a non-magnetizable, core 92 fixed pin 102, which serves as a stop for the armature 96, so that it does not abut the core 92 in its shifted position relative to the core 92, since this would lead to undesired adhesive forces.
  • the armature 96 mounted in a sliding sleeve 104 mounted in the flow housing 82 has a bore 106 through which the space between the armature 96 and the core 92 is connected to a space on the opposite side of the sliding sleeve 104, thereby preventing that in the interior of the solenoid valve 78 between the armature 96 and the core 92 existing fluid is compressed in the movement of the armature 96 in the direction of the core 92 and thus generates a force counteracting the movement. Instead, the fluid may drain through the bore 106.
  • the valve unit 86 consists of the flow housing 82 and a valve rod 108 fastened to the end of the armature 96, at the end of which the closing element 76 is fastened, which cooperates with two valve seats 110, 112 arranged in the flow housing 82, wherein the valve seat 110 also directly in the housing part 28 can be formed at the end of the receiving opening 80.
  • the closing member 76 has two closing surfaces 114, 116 formed at the opposite axial ends, of which the first closing surface 114 rests on the first valve seat 110 when the actuator 84 is not energized and the other closing surface 116 axially on the second valve seat when the actuator 84 is energized 112 rests.
  • the first valve seat 110 is disposed between a first flow port 118 of the flow housing 82, which is located in the housing part 28, and a second flow port 120
  • the second valve seat 112 is disposed between the second flow port 120 and a third flow port 122, so that either a connection exists between the first two flow ports 118, 120 or exists between the second and third flow ports 120, 122.
  • a first channel 124 in the form of a simple bore is formed in the housing part 28, which leads from the second flow port 120 into the first pressure chamber 72.
  • the first flow connection 118 opens into a second channel 126 formed in the housing part 28, which continues in the control pump housing 44 as far as the outlet 46 of the control pump 36.
  • the annular gap 60 at the outlet 62 of the coolant pump impeller 20 is fully released by the actuator 84 is not energized, whereby the closing member 76 due to the force of the spring 98 with its first closing surface 114th is pressed against the first valve seat 110, whereby the connection of the outlet 46 of the control pump 36 is interrupted to the first pressure chamber 72 and instead a connection of the second flow port 120 and thus of the first pressure chamber 72 to the third flow port 122 is released into a third channel 128th opens, which extends through the housing part 28 radially inward to the passage opening 48.
  • This passage opening 48 extends radially inside the control pump housing 44 through the entire control pump housing 44 to immediately behind theméffenpumpenank 20.
  • This has one or more axial bores 130 through which the coolant to the inlet 14 of the coolant pump 11 can flow, so that the coolant from the first pressure chamber is sucked through the coolant pump 11.
  • the closing of the first valve seat 110 has the consequence that the control pump 36 promotes against the closed first flow port 118. As a result, an increased pressure builds up in the entire flow channel 42, which also acts in the region of the inlet of the control pump 36.
  • a connecting channel 132 is formed in the form of a bore from the flow channel 42 to the second pressure chamber 74, so that this increased pressure builds up in the second pressure chamber 74.
  • This increased pressure in the second pressure chamber 74 has the result that at the bottom 66 of the control slide 56, a pressure difference arises, which causes the control slide 56 is displaced into its annular gap 60 releasing position and thus a maximum delivery of the coolant pump 11 is ensured.
  • An excessive increase in the pressure in the second pressure chamber 74 is avoided inter alia by a leakage between the control pump housing 44 and the peripheral wall 58, so that the additionally funded by the control pump 36 coolant is also used for promotion in the cooling circuit.
  • the solenoid valve 78 is energized again so that the pressure arising at the outlet 46 of the control pump 36 is again transferred to the first pressure chamber 72 is, while the pressure in the second pressure chamber 74 decreases, since in the region of the inlet by the suction of the refrigerant, a reduced pressure.
  • the coolant present in the second pressure chamber 74 is initially aspirated.
  • a pressure difference at the bottom 66 of the control slide 56 is correspondingly again, which causes the control slide 56 is moved into the annular gap 60 and thus the coolant flow in the Cooling circuit is interrupted.
  • a proportional or variable clocked solenoid 78 is used, which also makes it possible to drive the valve 78 in intermediate positions, so that for each position of the control spool 56 when using a proportional valve Force equilibrium can be achieved and according to a complete control of the flow cross-section of the annular gap 60 is made possible.
  • the pressure in the first and second pressure chamber 72, 74 is determined by the time ratio of the open and closed valve. Accordingly, the valve is driven in an oscillating manner via a frequency that is kept low so that the time throughput through the valve can be varied and regulated via the frequency. This allows even more precise control.
  • the described control arrangement is particularly compact by the integration of the solenoid valve and its execution as a 3/2-way valve, however, simple and inexpensive to produce and assemble.
  • On additional lines for hydraulic connection of the control pump with the pressure chambers of the control slide can be omitted, since they can be formed over very short distances as simple holes in the two inner housing parts.
  • the purely hydraulic adjustment of the control slide is very fast with short reaction times.
  • the position required for adjustment in the annular gap closing the control slide Required power reduced by eliminating the return spring, so that a faster adjustment with smaller cross-sections is possible.

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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)
  • Control Of Non-Positive-Displacement Pumps (AREA)
  • Multiple-Way Valves (AREA)
  • Magnetically Actuated Valves (AREA)

Description

Die Erfindung betrifft eine Regelanordnung für eine mechanisch regelbare Kühlmittelpumpe einer Verbrennungskraftmaschine mit einem verstellbaren Regelschieber, über den ein Durchströmungsquerschnitt eines Ringspalts zwischen einem Austritt eines Kühlmittelpumpenlaufrades und einem umgebenden Förderkanal regelbar ist, einer Regelpumpe, über die ein hydraulischer Druck erzeugbar ist, einem ersten Druckraum des Regelschiebers, der an einer ersten axialen Seite des Regelschiebers ausgebildet ist und einem Elektromagnetventil mit zwei Ventilsitzen und drei Strömungsanschlüssen sowie einem Schließglied, das mit einem Anker des Elektromagnetventils verbunden und axial bewegbar ist, wobei der erste Strömungsanschluss fluidisch mit einem Auslass der Regelpumpe verbunden ist und der zweite Strömungsanschluss mit dem ersten Druckraum des Regelschiebers fluidisch verbunden ist.The invention relates to a control arrangement for a mechanically controllable coolant pump of an internal combustion engine with an adjustable control slide, via which a flow cross section of an annular gap between an outlet of a Kühlmittelpumpenlaufrades and a surrounding conveyor channel is controllable, a control pump, via which a hydraulic pressure can be generated, a first pressure chamber of the A control slide, which is formed on a first axial side of the control slide and a solenoid valve having two valve seats and three flow ports and a closing member which is connected to an armature of the solenoid valve and axially movable, wherein the first flow port is fluidly connected to an outlet of the control pump and the second flow connection is fluidically connected to the first pressure chamber of the control slide.

Derartige Regelanordnungen für 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.Such control arrangements for 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 reduce fuel consumption, especially the cold running phase should of the engine are shortened. This is done, inter alia, by throttling or completely shutting off the coolant flow during this phase.

Zur Regelung der Kühlmittelmenge sind verschiedene Anordnungen 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 arrangements 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 Betätigung dieser Regelschieber 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 oder andersartig ausgeführten Druckraum, der mit einer Hydraulikflüssigkeit gefüllt wird, um bei dessen Füllung den Schieber über das Kühlmittelpumpenlaufrad zu verfahren. Eine Rückstellung des Regelschiebers erfolgt durch Öffnen des Druckraums zu einem Auslass, was zumeist über ein 2/2-Wege-Magnetventil erfolgt sowie unter Einwirkung einer Feder, die die Kraft zur Rückstellung des Schiebers zur Verfügung stellt.The operation of these control slide 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 or otherwise executed pressure chamber which is filled with a hydraulic fluid to move when filling the slide on the coolant pump impeller. A return of the control slide is done by opening the pressure chamber to an outlet, which is usually done via a 2/2-way solenoid valve and under the action of a spring, which provides the force to return the slide.

Um die zum Verfahren des Regelschiebers benötigte Kühlmittelmenge nicht über zusätzliche Fördereinheiten, wie zusätzliche Kolben/Zylindereinheiten zur Verfügung stellen zu müssen oder andere Hydraulikflüssigkeiten zur Betätigung verdichten zu müssen, sind Regelanordnungen bekannt geworden, bei denen eine den notwendigen Druck erzeugende Regelpumpe auf der Antriebswelle der Kühlmittelpumpe angeordnet ist, die entsprechend zur Verstellung des Schiebers dient. Diese Regelpumpen werden beispielsweise als Seitenkanalpumpen oder Servopumpen ausgeführt.In order not to have to provide the process of the control slide coolant amount on additional conveyor units, such as additional piston / cylinder units or compress other hydraulic fluids for actuation, control arrangements have become known in which a necessary pressure generating control pump on the drive shaft Coolant pump is arranged, which serves to adjust the slide accordingly. These control pumps are designed, for example, as side channel pumps or servo pumps.

Eine Regelanordnung für eine mechanisch angetriebene, regelbare Kühlmittelpumpe mit einer Regelpumpe, die einen Druck zur Verschiebung eines Regelschiebers erzeugt, 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 Regelpumpe 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. Entsprechend ist der erste Strömungsanschluss des Ventils mit dem Druckraum, der zweite Strömungsanschluss mit dem Auslass der Regelpumpe und der dritte Strömungsanschluss mit dem Zulauf der Regelpumpe verbunden. Eine detaillierte Kanal- und Strömungsführung der Regelanordnung wird nicht offenbart. Die schematisch dargestellten Strömungsführungen sind in modernen Verbrennungsmotoren technisch nur mit erhöhtem Aufwand und Bauraumbedarf realisierbar. Des Weiteren ist eine schnelle Entleerung des Kolbenraums nicht möglich, da die Entleerung zum Zulauf der Regelpumpe erfolgt, wodurch sich im gesamten Kanal ein Druck aufbaut, der im Kolbenraum als Gegendruck wirkt.A control arrangement for a mechanically driven, controllable coolant pump with a control pump, which generates a pressure for displacement of a control slide is known from DE 10 2012 207 387 A1 known. In this pump, a pressure side of the control 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. Correspondingly, the first flow connection of the valve to the pressure chamber, the second flow connection to the outlet of the control pump and the third flow connection to the inlet of the control pump. A detailed channel and flow guidance of the control arrangement is not disclosed. The flow guides shown schematically are technically feasible in modern internal combustion engines only with increased effort and space requirements. Furthermore, a quick emptying of the piston chamber is not possible because the emptying takes place to the inlet of the control pump, which builds up a pressure in the entire channel, which acts as a back pressure in the piston chamber.

Es stellt sich daher die Aufgabe, eine Regelanordnung für eine Kühlmittelpumpe einer Verbrennungskraftmaschine zu schaffen, welche möglichst kurze Schaltzeiten aufweist, so dass der geforderte Kühlmittelstrom möglichst unmittelbar zur Verfügung gestellt werden kann. Gleichzeitig soll der benötigte Bauraum minimiert werden. Eine Rückstellung des Schiebers in seine eine Maximalfördermenge der Kühlmittelpumpe sichernde Position soll möglichst ohne Verwendung einer auf den Regelschieber wirkenden Druckfeder erfolgen können. Des Weiteren sollte möglichst eine variable Steuerung des Kühlmittelstroms durchgeführt werden können.It is therefore the object to provide a control arrangement for a coolant pump of an internal combustion engine, which has the shortest possible switching times, so that the required coolant flow can be made available as directly as possible. At the same time the required space is to be minimized. A provision of the slide in its maximum flow rate of the coolant pump locking position should possible without use a force acting on the control slide compression spring can be done. Furthermore, a variable control of the coolant flow should be possible if possible.

Diese Aufgabe wird durch eine Regelanordnung für eine Kühlmittelpumpe eines Verbrennungsmotors mit den Merkmalen des Hauptanspruchs 1 gelöst.This object is achieved by a control arrangement for a coolant pump of an internal combustion engine with the features of the main claim 1.

Dadurch, dass der dritte Strömungsanschluss fluidisch mit einem Einlass der Kühlmittelpumpe verbunden ist, wobei der erste Ventilsitz zwischen dem ersten Strömungsanschluss und dem zweiten Strömungsanschluss ausgebildet ist und der zweite Ventilsitz zwischen dem zweiten Strömungsanschluss und dem dritten Strömungsanschluss ausgebildet ist, kann entweder eine Verbindung zwischen dem Druckraum und dem Einlass der Kühlmittelpumpe hergestellt werden, wodurch das dort vorhandene Kühlmittel schnell abgesaugt und damit der Druck im Druckraum schnell abgebaut werden kann oder eine Verbindung vom Auslass der Regelpumpe zum Druckraum hergestellt werden, wodurch eine Beaufschlagung des Druckraums und damit des Regelschiebers mit Druck erfolgt. Somit wird eine kurzfristige Verstellung des Regelschiebers durch Schalten des Elektromagnetventils ermöglicht.Characterized in that the third flow port is fluidly connected to an inlet of the coolant pump, wherein the first valve seat between the first flow port and the second flow port is formed and the second valve seat is formed between the second flow port and the third flow port, either a connection between the Pressure chamber and the inlet of the coolant pump are made, whereby the coolant there existing quickly sucked off and thus the pressure in the pressure chamber can be degraded quickly or a connection from the outlet of the control pump to the pressure chamber are made, whereby a pressurization of the pressure chamber and thus of the control slide , Thus, a short-term adjustment of the control slide is made possible by switching the solenoid valve.

Vorzugsweise weist das Elektromagnetventil ein Strömungsgehäuse, in dem das Schließglied axial zwischen den beiden Ventilsitzen bewegbar ist und einen elektromagnetischen Aktor mit einem Kern, Flussleitelementen, einer auf einem Spulenträger angeordneten Wicklung und den axial beweglichen Anker auf. Somit muss das Schließglied lediglich kurze Wege zurücklegen, wodurch die Schaltzeiten reduziert werden.The solenoid valve preferably has a flow housing in which the closing member is axially movable between the two valve seats and an electromagnetic actuator with a core, flux guide elements, a winding arranged on a coil carrier and the axially movable armature. Thus, the closing member only has to travel short distances, whereby the switching times are reduced.

In einer bevorzugten Ausführungsform ist zumindest das Strömungsgehäuse des Elektromagnetventils in einer Aufnahmeöffnung eines Gehäuseteils der Kühlmittelpumpe angeordnet. Entsprechend ist das Elektromagnetventil in unmittelbarer Nähe zur Regelpumpe anzuordnen, wodurch die Länge der Leitungen reduziert wird, was ebenfalls zu einer Verkürzung der Schaltzeiten der Regelanordnung führt. Zusätzlich wird wenig Bauraum benötigt und die Montage wird vereinfacht, da die gesamte Regelanordnung mit der Kühlmittelpumpe vormontiert und in das Außengehäuse eingesetzt werden kann.In a preferred embodiment, at least the flow housing of the solenoid valve is arranged in a receiving opening of a housing part of the coolant pump. Corresponding is to arrange the solenoid valve in close proximity to the control pump, whereby the length of the lines is reduced, which also leads to a shortening of the switching times of the control arrangement. In addition, little space is needed and the installation is simplified because the entire control arrangement can be pre-assembled with the coolant pump and inserted into the outer housing.

Vorteilhafterweise ist in dem Gehäuseteil ein erster Kanal ausgebildet, über den der erste Druckraum mit dem zweiten Strömungsanschluss verbunden ist. Zusätzliche Leitungen entfallen. Stattdessen werden extrem kurze Verbindungen für schnellere Schaltzeiten geschaffen.Advantageously, a first channel is formed in the housing part, via which the first pressure chamber is connected to the second flow connection. Additional lines are omitted. Instead, extremely short connections are created for faster switching times.

Zusätzlich ist es vorteilhaft, wenn in dem Gehäuseteil ein zweiter Kanal ausgebildet ist, der einerseits mit dem ersten Strömungsanschluss des Elektromagnetventils verbunden ist und sich andererseits im Regelpumpengehäuse bis zum Auslass der Regelpumpe fortsetzt. Somit müssen für die Verbindung zwischen Druckanschluss und Druckraum keine zusätzlichen Leitungen montiert werden, da diese Leitungen vollständig im Gehäuse integriert sind. Entsprechend weisen diese Verbindungen eine kurze Lauflänge auf.In addition, it is advantageous if in the housing part, a second channel is formed, which is on the one hand connected to the first flow port of the solenoid valve and on the other hand continues in the control pump housing to the outlet of the control pump. Thus, no additional lines must be mounted for the connection between pressure port and pressure chamber, since these lines are completely integrated in the housing. Accordingly, these compounds have a short run length.

Des Weiteren ist vorzugsweise in dem Gehäuseteil ein dritter Kanal ausgebildet, der einerseits mit dem dritten Strömungsanschluss des Elektromagnetventils verbunden ist und sich andererseits in eine radial innere Durchgangsöffnung des Gehäuseteils erstreckt, welche sich im Innern des Regelpumpengehäuses fortsetzt und durch die die Antriebswelle der Kühlmittelpumpe ragt, wobei im Kühlmittelpumpenlaufrad eine Axialbohrung ausgebildet ist, die zum Einlass der Kühlmittelpumpe führt. So wird auf einfache Weise auch die Verbindung zum Einlass der Kühlmittelpumpe mit nur einem zusätzlichen, insbesondere als Bohrung auszubildenden Kanal im Gehäuseteil und zumindest einer Bohrung im Kühlmittelpumpenlaufrad hergestellt. Auch diese Verbindung erfolgt ohne zusätzliche zu montierende Leitungen auf sehr kurzen Wegen.Furthermore, a third channel is preferably formed in the housing part, which is connected on the one hand to the third flow port of the solenoid valve and on the other hand extends into a radially inner passage opening of the housing part, which continues in the interior of the control pump housing and projects through the drive shaft of the coolant pump, wherein in the coolant pump impeller, an axial bore is formed, which leads to the inlet of the coolant pump. Thus, in a simple manner, the connection to the inlet of the coolant pump with only one additional channel to be formed, in particular as a bore, in the housing part and at least one bore in the coolant pump impeller is produced. Also This connection is made without additional cables to be mounted in a very short ways.

Vorzugsweise ist im Regelpumpengehäuse ein Kanal im Bereich eines Zulaufs der Regelpumpe ausgebildet, über den ein zweiter Druckraum mit dem Strömungskanal der Regelpumpe fluidisch verbunden ist, so dass die Kühlmittelpumpe ohne zusätzliche, eine stetige Kraft aufbringende Mittel, wie Druckfedern und ähnliches aufgebaut ist. Dies reduziert die erforderlichen Stellkräfte, wodurch erneut ein Schalten der Regelanordnung mit sehr kurzen Reaktionszeiten möglich wird.Preferably, in the control pump housing, a channel is formed in the region of an inlet of the control pump, via which a second pressure chamber is fluidically connected to the flow channel of the control pump, so that the coolant pump is constructed without additional, a continuous force applying means, such as compression springs and the like. This reduces the required control forces, which again switching the control arrangement with very short reaction times is possible.

In einer weiteren bevorzugten Ausbildung der Erfindung ist das Schließglied des Elektromagnetventils auf einer Ventilstange angeordnet, wobei eine Schließfläche an einem ersten axialen Ende des Schließgliedes dem ersten Ventilsitz zugeordnet ist und eine Schließfläche am entgegengesetzten axialen Ende dem zweiten Ventilsitz zugeordnet ist. Das axiale Aufliegen des Schließgliedes auf dem jeweiligen Ventilsitz führt zu einem dichten, beinahe leckagefreien Verschluss des jeweiligen Durchströmungsquerschnitts. Hierzu ist lediglich ein beidseitig belastetes Schließglied erforderlich, wodurch der Aufbau des Elektromagnetventils ebenfalls erleichtert wird.In a further preferred embodiment of the invention, the closing member of the solenoid valve is arranged on a valve rod, wherein a closing surface at a first axial end of the closing member is associated with the first valve seat and a closing surface is associated with the second valve seat at the opposite axial end. The axial bearing of the closing member on the respective valve seat leads to a dense, almost leak-free closure of the respective flow cross-section. For this purpose, only a double-loaded locking member is required, whereby the structure of the solenoid valve is also facilitated.

Das Elektromagnetventil ist dabei vorzugsweise als Proportionalventil ausgebildet. Dies ermöglicht eine stetige Regelung der Ventilöffnung, so dass der Regelschieber auch in Zwischenstellungen fahrbar ist und somit der Kühlmittelstrom vollständig geregelt werden kann. Diese Ventile wiesen eine hohe Lebensdauer auf, da das hochfrequente auftreffen des Ventilkörpers auf dem Ventilsitz entfällt.The solenoid valve is preferably designed as a proportional valve. This allows a continuous control of the valve opening, so that the control slide is movable in intermediate positions and thus the coolant flow can be completely controlled. These valves had a long service life, since the high-frequency impingement of the valve body on the valve seat is eliminated.

In einer hierzu alternativen Ausführungsform ist das Elektromagnetventil variabel getaktet ansteuerbar. Ein derartig angesteuertes Servoventil ist zwar teurer in der Herstellung, ermöglicht jedoch ein noch genaueres Regeln der gewünschten Öffnungsquerschnitte, so dass auch eine noch genauere Regelung der Stellung des Regelschiebers möglich wird.In an alternative embodiment, the solenoid valve is variable clocked controlled. Such a controlled servo valve is more expensive to manufacture, but allows an even more accurate Rules of the desired opening cross sections, so that even more accurate control of the position of the control slide is possible.

Es wird somit eine Regelanordnung für eine Kühlmittelpumpe einer Verbrennungskraftmaschine geschaffen, die eine hochgenaue und sehr schnelle Regelung des Kühlmittelstroms ermöglicht. Dabei wird nur ein geringer Bauraum benötigt und Montagezeiten deutlich reduziert. Insbesondere wird eine rein hydraulische Regelung der Stellung des Regelschiebers mit extrem kurzen Reaktionszeiten zur Verfügung gestellt.There is thus provided a control arrangement for a coolant pump of an internal combustion engine, which allows a highly accurate and very fast control of the coolant flow. Only a small space is required and installation times significantly reduced. In particular, a purely hydraulic control of the position of the control slide is provided with extremely short reaction times.

Ein Ausführungsbeispiel einer erfindungsgemäßen Kühlmittelpumpe für einen Verbrennungsmotor ist in den Figuren dargestellt und wird nachfolgend beschrieben.

  • Figur 1 zeigt eine Seitenansicht einer Kühlmittelpumpe mit erfindungsgemäßer Regelanordnung in geschnittener Darstellung.
  • Figur 2 zeigt eine Seitenansicht der Kühlmittelpumpe aus Figur 1 in zu Figur 1 gedrehter geschnittener Darstellung.
  • Figur 3 zeigt eine zu Figur 1 vergrößerte Darstellung eines 3/2-Wege-Elektromagnetventils einer erfindungsgemäßen Regelanordnung in geschnittener Darstellung.
An embodiment of a coolant pump according to the invention for an internal combustion engine is shown in the figures and will be described below.
  • FIG. 1 shows a side view of a coolant pump with inventive control arrangement in a sectional view.
  • FIG. 2 shows a side view of the coolant pump FIG. 1 in to FIG. 1 turned cut representation.
  • FIG. 3 shows one too FIG. 1 enlarged view of a 3/2-way solenoid valve of a control arrangement according to the invention in a sectional view.

Die dargestellte Kühlmittelpumpe 11 besteht aus einem Außengehäuse 10, in dem ein spiralförmiger Förderkanal 12 ausgebildet ist, in den über einen ebenfalls im Außengehäuse 10 ausgebildeten axialen Einlass 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 11 consists of an outer housing 10, in which a spiral conveying channel 12 is formed, in which a coolant is sucked in via an axial inlet 14 likewise formed in the outer housing 10, which coolant flows via the delivery channel 12 to a tangential pump outlet 16 formed in the outer housing 10 and 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. Der Antrieb des Kühlmittelpumpenlaufrades 20 erfolgt über einen Riemen 22, der in ein Riemenrad 24 greift, welches am zum Kühlmittelpumpenlaufrad 20 entgegengesetzten axialen Ende der Antriebswelle 18 befestigt ist. Das Riemenrad 24 ist über ein zweireihiges Kugellager 26 gelagert, welches auf einem feststehenden Gehäuseteil 28 aufgepresst ist, das am Außengehäuse 10 unter Zwischenlage einer Dichtung 30 befestigt ist. Zur Vorfixierung weist das Gehäuseteil 28 einen ringförmigen Vorsprung 32 auf, der in eine entsprechende Aufnahme des Außengehäuses 10 eingepasst ist.For this purpose, a coolant pump impeller 20 is fixed radially inside the conveying channel 12 on a drive shaft 18, which serves as Radialpumpenrad is formed by the rotation of the promotion of the coolant takes place in the conveying channel 12. The drive of the coolant pump impeller 20 via a belt 22 which engages in a pulley 24 which is secured to the coolant pump impeller 20 opposite axial end of the drive shaft 18. The pulley 24 is supported by a double-row ball bearing 26, which is pressed onto a stationary housing part 28, which is fastened to the outer housing 10 with the interposition of a seal 30. For prefixing, the housing part 28 has an annular projection 32, which is fitted into a corresponding receptacle of the outer housing 10.

Um nun die Kühlmittelpumpe 11 regeln zu können, ist an der zum Einlass 14 entgegengesetzten axialen Seite des Kühlmittelpumpenlaufrades 20 eine Regelanordnung 34 der Kühlmittelpumpe 11 ausgebildet. Diese besteht aus einer Regelpumpe 36 mit einem Regelpumpenlaufrad 38, welches einstückig mit dem Kühlmittelpumpenlaufrad 20 ausgebildet ist und entsprechend mit dem Kühlmittelpumpenlaufrad 20 gedreht wird. Dieses Regelpumpenlaufrad 38 weist Schaufeln 40 auf, die axial gegenüberliegend zu einem als Seitenkanal ausgebildeten Strömungskanal 42 angeordnet sind, der in einem Regelpumpengehäuse 44 ausgebildet ist. In diesem Regelpumpengehäuse 44 sind ein in dieser Darstellung nicht erkennbarer Zulauf und ein Auslass 46 ausgebildet, über welche das Kühlmittel einströmen beziehungsweise mit erhöhtem Druck ausströmen kann.In order to be able to control the coolant pump 11, a control arrangement 34 of the coolant pump 11 is formed on the axial side of the coolant pump impeller 20 opposite the inlet 14. This consists of a control pump 36 with a control pump impeller 38, which is integrally formed with the coolant pump impeller 20 and is rotated in accordance with the coolant pump impeller 20. This control pump impeller 38 has blades 40 which are arranged axially opposite to a flow channel 42 designed as a side channel, which is formed in a control pump housing 44. In this control pump housing 44 a not visible in this illustration inlet and an outlet 46 are formed, through which the coolant can flow or can flow at elevated pressure.

Das Regelpumpengehäuse 44 weist ebenso wie das Gehäuseteil 28 eine innere axiale Durchgangsöffnung 48 auf, durch die sich die Antriebswelle 18 unter Zwischenlage einer Dichtung 50 im Bereich des Gehäuseteils 28 erstreckt und ist am Gehäuseteil 28 befestigt. Hierzu ist am Regelpumpengehäuse 44 ein zum Gehäuseteil 28 weisender ringförmiger Vorsprung 52 ausgebildet, der in eine entsprechende Aufnahmeöffnung 49 des Gehäuseteils 28 ragt, wodurch eine Vorfixierung erfolgt. Anschließend wird das Regelpumpengehäuse 44 über Schrauben 54, die sich durch das Regelpumpengehäuse 44 in entsprechende Gewindebohrungen des Gehäuseteils 28 erstrecken, befestigt.The control pump housing 44 has, just like the housing part 28, an inner axial through opening 48, through which the drive shaft 18 extends with the interposition of a seal 50 in the region of the housing part 28 and is fastened to the housing part 28. For this purpose, a ring-shaped projection 52 facing the housing part 28 is formed on the control pump housing 44, which protrudes into a corresponding receiving opening 49 of the housing part 28, whereby a prefixing takes place. Subsequently, the control pump housing 44 via screws 54, the extend through the control pump housing 44 into corresponding threaded bores of the housing part 28, attached.

Die Regelung der geförderten Kühlmittelmenge der Kühlmittelpumpe 11 erfolgt über einen Regelschieber 56, dessen zylindrische Umfangswand 58 derart über das Kühlmittelpumpenlaufrad 20 geschoben werden kann, dass ein freier Querschnitt eines Ringspalts 60 zwischen einem Austritt 62 des Kühlmittelpumpenlaufrades 20 und dem Förderkanal 12 geregelt wird. Die Bewegung des Regelschiebers 56 wird einerseits durch das Ende des Ringspalts 60, andererseits durch den Vorsprung 32 begrenzt, gegen dessen axiales Ende ein Absatz 64 der Umfangswand 58 in der vollständig den Ringspalt 60 freigebenden Stellung des Regelschiebers 56 anliegt.The control of the conveyed coolant quantity of the coolant pump 11 via a control slide 56, the cylindrical peripheral wall 58 can be pushed over the coolant pump impeller 20 so that a free cross section of an annular gap 60 between an outlet 62 of the coolant pump impeller 20 and the delivery channel 12 is controlled. The movement of the control slide 56 is limited on the one hand by the end of the annular gap 60, on the other hand by the projection 32, against the axial end of a shoulder 64 of the peripheral wall 58 in the completely releasing the annular gap 60 position of the control slide 56 is applied.

Der Regelschieber 56 weist neben der Umfangswand 58 einen Boden 66 auf, von dessen Außenumfang aus sich die Umfangswand 58 axial zwischen dem Regelpumpengehäuse 44 und dem Außengehäuse 10 in Richtung des sich axial anschließenden Ringspaltes 60 erstreckt. Im radial inneren Bereich weist der Boden 66 eine Öffnung 68 auf, die durch einen hohlzylindrischen Abschnitt 70 begrenzt wird, über den der Regelschieber 56 auf dem Regelpumpengehäuse 44 gelagert wird. Am äußeren und am inneren Umfang des Bodens 66 ist jeweils eine Radialnut ausgebildet, in der jeweils ein Kolbenring 71 angeordnet ist, über die die beiden axial gegenüberliegenden Seiten des Regelschiebers 56 zueinander abgedichtet werden.The control slide 56 has, in addition to the peripheral wall 58, a bottom 66, from the outer periphery of which the circumferential wall 58 extends axially between the control pump housing 44 and the outer housing 10 in the direction of the axially adjoining annular gap 60. In the radially inner region of the bottom 66 has an opening 68 which is delimited by a hollow cylindrical portion 70, via which the control slide 56 is mounted on the control pump housing 44. On the outer and inner circumference of the bottom 66, a radial groove is formed, in each of which a piston ring 71 is arranged, via which the two axially opposite sides of the control slide 56 are sealed to one another.

An der vom Kühlmittelpumpenlaufrad 20 abgewandten Seite des Regelschiebers 56 befindet sich ein erster Druckraum 72, der axial durch das Gehäuseteil 28 und den Boden 66 des Regelschiebers 56 und radial nach außen durch das Außengehäuse 10 beziehungsweise den ringförmigen Vorsprung 32 des Gehäuseteils 28 und nach radial innen durch das Regelpumpengehäuse 44 begrenzt wird. An der zum Kühlmittelpumpenlaufrad 20 gewandten Seite des Bodens 66 wird ein zweiter Druckraum 74 gebildet, der axial durch den Boden 66 und das Regelpumpengehäuse 44, nach radial außen durch die Umfangswand 58 des Regelschiebers 56 und nach radial innen durch das Regelpumpengehäuse 44 begrenzt wird. Je nach am Boden 66 des Regelschiebers 56 in den beiden Druckräumen 72, 74 anliegender Druckdifferenz wird die Umfangswand 58 des Regelschiebers 56 entsprechend in den Ringspalt 60 hinein- oder aus dem Ringspalt 60 herausgeschoben.At the side facing away from the coolant pump impeller 20 side of the control slide 56 is a first pressure chamber 72, axially through the housing part 28 and the bottom 66 of the control slide 56 and radially outwardly through the outer housing 10 and the annular projection 32 of the housing part 28 and radially inward is limited by the control pump housing 44. On the side facing the coolant pump impeller 20 side of the bottom 66, a second pressure chamber 74 is formed axially through the bottom 66 and the Rule pump housing 44 is limited radially outward by the peripheral wall 58 of the control slide 56 and radially inwardly by the control pump housing 44. Depending on the bottom 66 of the control slide 56 in the two pressure chambers 72, 74 adjacent pressure difference, the peripheral wall 58 of the control slide 56 in accordance with the annular gap 60 in or out of the annular gap 60 pushed out.

Die hierzu notwendige Druckdifferenz wird durch die Regelpumpe 36 erzeugt, wobei der entsprechende Druck in Abhängigkeit der Stellung eines Schließgliedes 76 eines 3/2-Wege-Elektromagnetventils 78 dem jeweiligen Druckraum 72, 74 zugeführt wird. Hierzu ist im Gehäuseteil 28 eine Aufnahmeöffnung 80 für das Elektromagnetventil 78 ausgebildet, in welcher ein Strömungsgehäuse 82 des Elektromagnetventils 78 aufgenommen wird.The required pressure difference is generated by the control pump 36, wherein the corresponding pressure in response to the position of a closing member 76 of a 3/2-way solenoid valve 78 to the respective pressure chamber 72, 74 is supplied. For this purpose, a receiving opening 80 for the solenoid valve 78 is formed in the housing part 28, in which a flow housing 82 of the solenoid valve 78 is received.

Das Elektromagnetventil 78 ist in der Figur 3 dargestellt. Es besteht aus einem elektromagnetischen Aktor 84 sowie einer Ventileinheit 86. Der Aktor 84 weist eine auf einem Spulenträger 88 angeordnete Wicklung 90 auf, in deren Innern sich ein Kern 92 befindet und welche axial und radial von Flussleitelementen 94 des elektromagnetischen Kreises umgeben ist. Bei Bestromung der Wicklung 90 wird ein axial beweglicher Anker 96 in Richtung des Kerns 92 gezogen. Diese Bewegung erfolgt entgegen der Kraft einer Feder 98, welche zwischen dem Kern 92 und dem Anker 96 in einer Ausnehmung 100 am Kern 92 angeordnet ist und einen nicht magnetisierbaren, im Kern 92 befestigten Stift 102 umgibt, der als Anschlag für den Anker 96 dient, so dass dieser in seiner zum Kern 92 verschobenen Position nicht am Kern 92 anliegt, da dies zu unerwünschten Klebekräften führen würde. Der in einer im Strömungsgehäuse 82 befestigten Gleithülse 104 gelagerte Anker 96 weist eine Bohrung 106 auf, über die der Raum zwischen dem Anker 96 und dem Kern 92 mit einem Raum an der zur Gleithülse 104 entgegengesetzten Seite verbunden ist, wodurch verhindert wird, dass das im Innern des Elektromagnetventils 78 zwischen dem Anker 96 und dem Kern 92 vorhandene Fluid bei der Bewegung des Ankers 96 in Richtung des Kerns 92 komprimiert wird und so eine der Bewegung entgegen wirkende Kraft erzeugt. Stattdessen kann das Fluid durch die Bohrung 106 abfließen.The solenoid valve 78 is in the FIG. 3 shown. It consists of an electromagnetic actuator 84 and a valve unit 86. The actuator 84 has a winding 90 arranged on a coil support 88, in the interior of which there is a core 92 and which is surrounded axially and radially by flux-conducting elements 94 of the electromagnetic circuit. When current flows through the winding 90, an axially movable armature 96 is pulled in the direction of the core 92. This movement takes place counter to the force of a spring 98, which is arranged between the core 92 and the armature 96 in a recess 100 on the core 92 and surrounds a non-magnetizable, core 92 fixed pin 102, which serves as a stop for the armature 96, so that it does not abut the core 92 in its shifted position relative to the core 92, since this would lead to undesired adhesive forces. The armature 96 mounted in a sliding sleeve 104 mounted in the flow housing 82 has a bore 106 through which the space between the armature 96 and the core 92 is connected to a space on the opposite side of the sliding sleeve 104, thereby preventing that in the interior of the solenoid valve 78 between the armature 96 and the core 92 existing fluid is compressed in the movement of the armature 96 in the direction of the core 92 and thus generates a force counteracting the movement. Instead, the fluid may drain through the bore 106.

Die Ventileinheit 86 besteht aus dem Strömungsgehäuse 82 sowie einer am Ende des Ankers 96 befestigten Ventilstange 108, an deren Ende das Schließglied 76 befestigt ist, welches mit zwei im Strömungsgehäuse 82 angeordneten Ventilsitzen 110, 112 zusammenwirkt, wobei der Ventilsitz 110 auch direkt im Gehäuseteil 28 am Ende der Aufnahmeöffnung 80 ausgebildet werden kann. Hierzu weist das Schließglied 76 zwei an den gegenüberliegenden axialen Enden ausgebildete Schließflächen 114, 116 auf, von denen die erste Schließfläche 114 auf dem ersten Ventilsitz 110 bei nicht bestromtem Aktor 84 aufliegt und die andere Schließfläche 116 bei Bestromung des Aktors 84 axial auf dem zweiten Ventilsitz 112 aufliegt.The valve unit 86 consists of the flow housing 82 and a valve rod 108 fastened to the end of the armature 96, at the end of which the closing element 76 is fastened, which cooperates with two valve seats 110, 112 arranged in the flow housing 82, wherein the valve seat 110 also directly in the housing part 28 can be formed at the end of the receiving opening 80. For this purpose, the closing member 76 has two closing surfaces 114, 116 formed at the opposite axial ends, of which the first closing surface 114 rests on the first valve seat 110 when the actuator 84 is not energized and the other closing surface 116 axially on the second valve seat when the actuator 84 is energized 112 rests.

Der erste Ventilsitz 110 ist zwischen einem ersten Strömungsanschluss 118 des Strömungsgehäuses 82, welcher sich im Gehäuseteil 28 befindet, und einem zweiten Strömungsanschluss 120 angeordnet, der zweite Ventilsitz 112 ist zwischen dem zweiten Strömungsanschluss 120 und einem dritten Strömungsanschluss 122 angeordnet, so dass entweder eine Verbindung zwischen den ersten beiden Strömungsanschlüssen 118, 120 besteht oder zwischen dem zweiten und dritten Strömungsanschluss 120, 122 besteht. Um den ersten Druckraum 72 mit unter Druck stehenden Fluid versorgen zu können, ist im Gehäuseteil 28 ein erster Kanal 124 in Form einer einfachen Bohrung ausgebildet, der vom zweiten Strömungsanschluss 120 in den ersten Druckraum 72 führt. Der erste Strömungsanschluss 118 mündet in einen im Gehäuseteil 28 ausgebildeten zweiten Kanal 126, der sich im Regelpumpengehäuse 44 bis zum Auslass 46 der Regelpumpe 36 fortsetzt. Bei fluidischer Verbindung des ersten Strömungsanschlusses 118 mit dem zweiten Strömungsanschluss 120 wird entsprechend der erste Druckraum 72 über die Kanäle 124, 126 mit dem unter Druck stehenden Fluid aus dem Strömungskanal 42 der Regelpumpe 36 versorgt, wodurch der Regelschieber in seine den Ringspalt 60 verschließende Stellung geschoben wird. Dies erfolgt, wenn das Schließglied 76 mit seiner zweiten Schließfläche 116 auf dem zweiten Ventilsitz 112 aufliegt, was erfolgt, wenn der Aktor 84 bestromt wird und entsprechend sich der Anker in seiner zurückgezogenen Position befindet. Der Regelschieber 56 wird entsprechend vollständig in den Ringspalt 60 verschoben, so dass die Kühlmittelförderung der Kühlmittelpumpe 11 unterbunden wird.The first valve seat 110 is disposed between a first flow port 118 of the flow housing 82, which is located in the housing part 28, and a second flow port 120, the second valve seat 112 is disposed between the second flow port 120 and a third flow port 122, so that either a connection exists between the first two flow ports 118, 120 or exists between the second and third flow ports 120, 122. In order to be able to supply the first pressure chamber 72 with fluid under pressure, a first channel 124 in the form of a simple bore is formed in the housing part 28, which leads from the second flow port 120 into the first pressure chamber 72. The first flow connection 118 opens into a second channel 126 formed in the housing part 28, which continues in the control pump housing 44 as far as the outlet 46 of the control pump 36. With fluidic connection of the first flow port 118 with the second Flow connection 120 is supplied via the channels 124, 126 with the pressurized fluid from the flow channel 42 of the control pump 36 corresponding to the first pressure chamber 72, whereby the control slide is pushed into its the annular gap 60 occlusive position. This occurs when the closing member 76 rests with its second closing surface 116 on the second valve seat 112, which takes place when the actuator 84 is energized and, accordingly, the armature is in its retracted position. The control slide 56 is correspondingly moved completely into the annular gap 60, so that the coolant delivery of the coolant pump 11 is prevented.

Soll die Kühlmittelpumpe 11 im Betrieb eine maximale Kühlmittelmenge zum Pumpenauslass 16 fördern, wird der Ringspalt 60 am Austritt 62 des Kühlmittelpumpenlaufrades 20 vollständig freigegeben, indem der Aktor 84 nicht bestromt wird, wodurch das Schließglied 76 aufgrund der Kraft der Feder 98 mit seiner ersten Schließfläche 114 gegen den ersten Ventilsitz 110 gedrückt wird, wodurch die Verbindung des Auslasses 46 der Regelpumpe 36 zum ersten Druckraum 72 unterbrochen wird und stattdessen eine Verbindung des zweiten Strömungsanschlusses 120 und damit des ersten Druckraums 72 zum dritten Strömungsanschluss 122 freigegeben wird, der in einen dritten Kanal 128 mündet, der sich durch das Gehäuseteil 28 nach radial innen bis zur Durchgangsöffnung 48 erstreckt. Diese Durchgangsöffnung 48 erstreckt sich radial innerhalb des Regelpumpengehäuses 44 durch das gesamte Regelpumpengehäuse 44 bis unmittelbar hinter das Kühlmittelpumpenlaufrad 20. Dieses weist ein oder mehrere Axialbohrungen 130 auf, durch die das Kühlmittel zum Einlass 14 der Kühlmittelpumpe 11 strömen kann, so dass das Kühlmittel aus dem ersten Druckraum durch die Kühlmittelpumpe 11 abgesaugt wird. Das Schließen des ersten Ventilsitzes 110 hat zur Folge, dass die Regelpumpe 36 gegen den verschlossenen ersten Strömungsanschluss 118 fördert. Hierdurch baut sich im gesamten Strömungskanal 42 ein erhöhter Druck auf, der auch im Bereich des Zulaufs der Regelpumpe 36 wirkt. Im Bereich dieses Zulaufs ist jedoch im Regelpumpengehäuse 44 ein Verbindungskanal 132 in Form einer Bohrung vom Strömungskanal 42 zum zweiten Druckraum 74 ausgebildet, so dass sich dieser erhöhte Druck auch im zweiten Druckraum 74 aufbaut. Dieser erhöhte Druck im zweiten Druckraum 74 hat zur Folge, dass am Boden 66 des Regelschiebers 56 eine Druckdifferenz entsteht, die dazu führt, dass der Regelschieber 56 in seine den Ringspalt 60 freigebende Position verschoben wird und somit eine Maximalförderung der Kühlmittelpumpe 11 sichergestellt wird.If the coolant pump 11 in operation to promote a maximum amount of coolant to the pump outlet 16, the annular gap 60 at the outlet 62 of the coolant pump impeller 20 is fully released by the actuator 84 is not energized, whereby the closing member 76 due to the force of the spring 98 with its first closing surface 114th is pressed against the first valve seat 110, whereby the connection of the outlet 46 of the control pump 36 is interrupted to the first pressure chamber 72 and instead a connection of the second flow port 120 and thus of the first pressure chamber 72 to the third flow port 122 is released into a third channel 128th opens, which extends through the housing part 28 radially inward to the passage opening 48. This passage opening 48 extends radially inside the control pump housing 44 through the entire control pump housing 44 to immediately behind the Kühlmittelpumpenlaufrad 20. This has one or more axial bores 130 through which the coolant to the inlet 14 of the coolant pump 11 can flow, so that the coolant from the first pressure chamber is sucked through the coolant pump 11. The closing of the first valve seat 110 has the consequence that the control pump 36 promotes against the closed first flow port 118. As a result, an increased pressure builds up in the entire flow channel 42, which also acts in the region of the inlet of the control pump 36. In the area of this inlet, however, is in the control pump housing 44th a connecting channel 132 is formed in the form of a bore from the flow channel 42 to the second pressure chamber 74, so that this increased pressure builds up in the second pressure chamber 74. This increased pressure in the second pressure chamber 74 has the result that at the bottom 66 of the control slide 56, a pressure difference arises, which causes the control slide 56 is displaced into its annular gap 60 releasing position and thus a maximum delivery of the coolant pump 11 is ensured.

Bei einem Ausfall der elektrischen Versorgung des Magnetventils 78 nimmt der Regelschieber 56 entsprechend die gleiche Position ein, so dass auch in diesem Notlaufbetriebszustand eine Maximalförderung der Kühlmittelpumpe 11 sichergestellt wird, ohne dass hierzu eine Rückstellfeder oder eine andere, nicht hydraulische Kraft notwendig wäre.In case of failure of the electrical supply of the solenoid valve 78 of the control slide 56 assumes the same position, so that even in this emergency operation, a maximum promotion of the coolant pump 11 is ensured without the need for a return spring or other, non-hydraulic force would be necessary.

Eine zu starke Erhöhung des Drucks im zweiten Druckraum 74 wird unter anderem durch eine Leckage zwischen dem Regelpumpengehäuse 44 und der Umfangswand 58 vermieden, so dass das zusätzlich durch die Regelpumpe 36 geförderte Kühlmittel ebenfalls zur Förderung in den Kühlkreislauf genutzt wird.An excessive increase in the pressure in the second pressure chamber 74 is avoided inter alia by a leakage between the control pump housing 44 and the peripheral wall 58, so that the additionally funded by the control pump 36 coolant is also used for promotion in the cooling circuit.

Wird wieder ein reduzierter Kühlmittelstrom von der Motorsteuerung gefordert, wie dies beispielsweise während des Warmlaufs des Verbrennungsmotors nach dem Kaltstart der Fall ist, wird das Magnetventil 78 wieder bestromt, so dass erneut der am Auslass 46 der Regelpumpe 36 entstehende Druck in den ersten Druckraum 72 übertragen wird, während gleichzeitig der Druck im zweiten Druckraum 74 sinkt, da im Bereich des Zulaufs durch das Ansaugen des Kühlmittels ein verringerter Druck entsteht. Dabei wird zunächst auch das im zweiten Druckraum 74 vorhandene Kühlmittel abgesaugt. In diesem Zustand liegt entsprechend erneut eine Druckdifferenz am Boden 66 des Regelschiebers 56 an, die dazu führt, dass der Regelschieber 56 in den Ringspalt 60 verschoben wird und somit der Kühlmittelstrom im Kühlkreislauf unterbrochen wird. Bei erhöhtem Druckaufbau im ersten Druckraum 72 steigt zwar nach einiger Zeit auch der Druck im Strömungskanal 42 und im zweiten Druckraum 74, was jedoch nicht zu einer Rückstellung führt, da die Leckage aus dem zweiten Druckraum 74 größer ist als aus dem ersten Druckraum 72 und zur Verstellung zusätzlich eine Reibungskraft zu überwinden wäre. Entsprechend verbleibt der Regelschieber 56 in der gewünschten Position, ohne dass eine zu starke Druckerhöhung entsteht.If a reduced coolant flow is again demanded 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 78 is energized again so that the pressure arising at the outlet 46 of the control pump 36 is again transferred to the first pressure chamber 72 is, while the pressure in the second pressure chamber 74 decreases, since in the region of the inlet by the suction of the refrigerant, a reduced pressure. In this case, the coolant present in the second pressure chamber 74 is initially aspirated. In this state, a pressure difference at the bottom 66 of the control slide 56 is correspondingly again, which causes the control slide 56 is moved into the annular gap 60 and thus the coolant flow in the Cooling circuit is interrupted. With increased pressure build-up in the first pressure chamber 72, although after some time, the pressure in the flow channel 42 and in the second pressure chamber 74, but this does not lead to a provision, since the leakage from the second pressure chamber 74 is greater than from the first pressure chamber 72 and Adjustment additionally a friction force would be overcome. Accordingly, the control slide 56 remains in the desired position, without causing an excessive pressure increase.

Um zusätzlich eine vollständige Regelbarkeit des geförderten Kühlmittelstroms zu erhalten, wird ein proportional arbeitendes oder ein variabel getaktetes Magnetventil 78 verwendet, wodurch es auch möglich wird, das Ventil 78 in Zwischenstellungen zu fahren, so dass für jede Position des Regelschiebers 56 bei Nutzung eines Porportionalventils ein Kräftegleichgewicht erzielbar ist und entsprechend eine vollständige Regelung des Durchströmungsquerschnitts des Ringspaltes 60 ermöglicht wird. Beim getakteten Magnetventil wird der Druck im ersten und zweiten Druckraum 72, 74 durch das zeitliche Verhältnis von geöffnetem und geschlossenem Ventil bestimmt. Entsprechend wird über eine niedrig gehaltene Frequenz das Ventil oszillierend angesteuert, so dass über die Frequenz der zeitliche Durchsatz über das Ventil variiert und geregelt werden kann. Dies ermöglicht eine noch genauere Regelung.In addition, to obtain complete controllability of the delivered coolant flow, a proportional or variable clocked solenoid 78 is used, which also makes it possible to drive the valve 78 in intermediate positions, so that for each position of the control spool 56 when using a proportional valve Force equilibrium can be achieved and according to a complete control of the flow cross-section of the annular gap 60 is made possible. When clocked solenoid valve, the pressure in the first and second pressure chamber 72, 74 is determined by the time ratio of the open and closed valve. Accordingly, the valve is driven in an oscillating manner via a frequency that is kept low so that the time throughput through the valve can be varied and regulated via the frequency. This allows even more precise control.

Die beschriebene Regelanordnung ist insbesondere durch die Integration des Elektromagnetventils und dessen Ausführung als 3/2-Wege-Ventil äußerst kompakt aufgebaut, jedoch einfach und kostengünstig herstellbar und montierbar. Auf zusätzliche Leitungen zur hydraulischen Verbindung der Regelpumpe mit den Druckräumen des Regelschiebers kann verzichtet werden, da diese über sehr kurze Wege als einfache Bohrungen in den beiden inneren Gehäuseteilen ausgebildet werden können. Die rein hydraulische Verstellung des Regelschiebers erfolgt sehr schnell mit kurzen Reaktionszeiten. Zusätzlich wird der zur Verstellung in die den Ringspalt verschließende Position des Regelschiebers benötigte Kraftbedarf durch den Wegfall der Rückstellfeder reduziert, so dass eine schnellere Verstellung mit kleineren Querschnitten möglich ist.The described control arrangement is particularly compact by the integration of the solenoid valve and its execution as a 3/2-way valve, however, simple and inexpensive to produce and assemble. On additional lines for hydraulic connection of the control pump with the pressure chambers of the control slide can be omitted, since they can be formed over very short distances as simple holes in the two inner housing parts. The purely hydraulic adjustment of the control slide is very fast with short reaction times. In addition, the position required for adjustment in the annular gap closing the control slide Required power reduced by eliminating the return spring, so that a faster adjustment with smaller cross-sections is possible.

Es sollte deutlich sein, dass der Schutzbereich des Hauptanspruchs nicht auf das beschriebene Ausführungsbeispiel begrenzt ist. Insbesondere sind andere Gehäuseteilungen einer anders ausgeführten Regelpumpe denkbar. Auch die Kanalführungen oder die Begrenzungen der Druckräume können geändert werden, ohne den Schutzbereich des Hauptanspruchs zu verlassen. Zusätzlich ist beispielsweise eine zweistückige Ausbildung der beiden Pumpenlaufräder denkbar.It should be clear that the scope of the main claim is not limited to the embodiment described. In particular, other housing divisions of a differently designed control pump are conceivable. Also, the ducts or the boundaries of the pressure chambers can be changed without departing from the scope of the main claim. In addition, for example, a two-piece design of the two pump impellers is conceivable.

Claims (10)

  1. A control arrangement for a mechanically controllable coolant pump of an internal combustion engine having
    an adjustable control slide (56) by means of which a throughflow cross-section of an annular gap (60) between an outlet (62) of a coolant pump impeller (20) and a surrounding delivery duct (22) is controllable,
    a control pump (36) by means of which a hydraulic pressure is adapted to be generated in a flow duct (42),
    a first pressure chamber (72) of said control slide (56), which is formed on a first axial side of said control slide (56),
    an electromagnetic valve (78) having two valve seats (110, 112) and three flow connections (118, 120, 122) as well as a closing member (76) which is connected to an armature (96) of said electromagnetic valve (78) and is adapted to be axially moved,
    wherein said first flow connection (118) is fluidically connected to an outlet (46) of said control pump (36) and said second flow connection (120) is fluidically connected to said first pressure chamber (72) of said control slide (56),
    characterized in that
    said third flow connection (122) is fluidically connected to an inlet (14) of said coolant pump (11), wherein said first valve seat (110) is formed between said first flow connection (118) and said second flow connection (120) and said second valve seat (112) is formed between said second flow connection (120) and said third flow connection(122).
  2. The control arrangement for a mechanically controllable coolant pump of an internal combustion engine according to claim 1,
    characterized in that
    the electromagnetic valve (78) comprises a flow housing (82) in which the closing member (76) is axially movable between the two valve seats (110, 112), and an electromagnetic actuator (84) having a core (92), flow-conducting elements (94), a winding (90) arranged on a coil carrier (88) and the axially movable armature (96).
  3. The control arrangement for a mechanically controllable coolant pump of an internal combustion engine according to claim 2,
    characterized in that
    at least the flow housing (82) of the electromagnetic valve (78) is arranged in an accommodation opening (80) of a housing part (28) of the coolant pump (11).
  4. The control arrangement for a mechanically controllable coolant pump of an internal combustion engine according to claim 3,
    characterized in that
    in the housing part (28) a first duct (124) is formed via which the first pressure chamber (72) is connected to the second flow connection (120).
  5. The control arrangement for a mechanically controllable coolant pump of an internal combustion engine according to any one of claims 3 or 4,
    characterized in that
    in the housing part (28) a second duct (126) is formed which on the one hand is connected to the first flow connection (118) of the electromagnetic valve (78) and on the other hand continues in the control pump housing (44) up to the outlet (46) of control pump (36).
  6. The control arrangement for a mechanically controllable coolant pump of an internal combustion engine according to any one of claims 3 to 5,
    characterized in that
    in the housing part (28) a third duct (128) is formed which on the one hand is connected to the third flow connection (122) of the electromagnetic valve (78) and on the other hand extends into a radially inner through-going opening (48) of the housing part (28) continuing inside the control pump housing (44) and through which a drive shaft (18) of the coolant pump (11) extends, wherein in the coolant pump impeller (20) at least one axial bore (130) is formed which extends to the inlet (14) of the coolant pump (11).
  7. The control arrangement for a mechanically controllable coolant pump of an internal combustion engine according to any one of the preceding claims,
    characterized in that
    in a control pump housing (44) a connecting duct (132) is formed in the area of an inlet of the control pump (36), via which a second pressure chamber (74) is fluidically connected to the flow duct (42) of said control pump (36).
  8. The control arrangement for a mechanically controllable coolant pump of an internal combustion engine according to any one of the preceding claims,
    characterized in that
    the closing member (76) of the electromagnetic valve (78) is fastened to a valve rod (108), wherein a closing surface (114) at a first axial end of said closing member (76) is associated with the first valve seat (110) and a closing surface (116) at the opposite axial end is associated with the second valve seat (112).
  9. The control arrangement for a mechanically controllable coolant pump of an internal combustion engine according to any one of the preceding claims,
    characterized in that
    the electromagnetic valve (78) is a proportional valve.
  10. The control arrangement for a mechanically controllable coolant pump of an internal combustion engine according to any one of claims 1 to 7,
    characterized in that
    the electromagnetic valve (78) is adapted to be driven in a variably clocked manner.
EP16785429.8A 2015-11-06 2016-10-19 Control arrangement for a mechanically controllable coolant pump of an internal combustion engine Active EP3371463B1 (en)

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PCT/EP2016/075072 WO2017076644A1 (en) 2015-11-06 2016-10-19 Control arrangement for a mechanically controllable coolant pump of an internal combustion engine

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DE102015119098B4 (en) 2019-03-21
DE102015119098A1 (en) 2017-05-11
US11181112B2 (en) 2021-11-23
CN108350890A (en) 2018-07-31
JP6647540B2 (en) 2020-02-14
US20180320694A1 (en) 2018-11-08
JP2019500532A (en) 2019-01-10
CN108350890B (en) 2020-02-14
EP3371463A1 (en) 2018-09-12
WO2017076644A1 (en) 2017-05-11

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