EP3371461B1 - Coolant pump for an internal combustion engine - Google Patents

Coolant pump for an internal combustion engine Download PDF

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Publication number
EP3371461B1
EP3371461B1 EP16782281.6A EP16782281A EP3371461B1 EP 3371461 B1 EP3371461 B1 EP 3371461B1 EP 16782281 A EP16782281 A EP 16782281A EP 3371461 B1 EP3371461 B1 EP 3371461B1
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EP
European Patent Office
Prior art keywords
housing part
coolant pump
side channel
internal combustion
combustion engine
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
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Application number
EP16782281.6A
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German (de)
French (fr)
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EP3371461A1 (en
Inventor
Stephan Zielberg
Andreas Burger
Michael-Thomas Benra
Stefan Rothgang
Michael Becker
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Pierburg GmbH
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Pierburg GmbH
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Publication of EP3371461A1 publication Critical patent/EP3371461A1/en
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D15/00—Control, e.g. regulation, of pumps, pumping installations or systems
    • F04D15/0027—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
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D5/00—Pumps with circumferential or transverse flow
    • F04D5/002—Regenerative pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • 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
    • F01P3/00—Liquid cooling
    • F01P2003/001—Cooling liquid
    • 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 coolant pump for an internal combustion engine with a drive shaft, a coolant pump impeller, which is at least rotationally fixed on the drive shaft and via which coolant in a surrounding the coolant pump impeller conveyor is conveyed, an adjustable control slide, via which a flow cross section of an annular gap between an outlet of theméffenpumpenlaufrades and the delivery channel is controllable, a side channel pump with a sokanalpumpenlaufrad which is rotatably mounted on the drive shaft, a side channel of the side channel pump in which by rotation of the 10%pumpenlaufrades a pressure can be generated, a pressure channel through which an outlet of the side channel with a first Pressure chamber of the control slide is fluidically connectable, and a valve, via which a flow cross-section of the pressure channel can be closed and released.
  • Such 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.
  • Coolant pumps 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 to compress other hydraulic fluids for actuation, are mechanically controllable Coolant pumps have become known, on the drive shaft, a second delivery wheel is arranged, via which the pressure for adjusting the slide is provided. These pumps are designed, for example, as side channel pumps or servo pumps.
  • Such a coolant device with a secondary pump acting as a secondary pump is from the DE 10 2012 207 387 A1 known.
  • This pump is located at the back of the pump, a slider which is displaceable by a pressure in an annular chamber and can be reset by a spring.
  • This annular chamber is formed in a housing, which in turn is arranged on the back of the slide and in which a first side channel of the side channel pump is arranged, which is arranged correspondingly opposite to the arranged on the shaft side channel pump impeller.
  • a second side channel is formed in a further housing part.
  • a pressure side of the side channel pump is closed in this pump in a first position and a suction side of the pump connected to the cooling circuit and the slider and in a second position, the pressure side with the annular chamber of the slide and the suction side with the cooling circuit connected.
  • a detailed channel and flow guidance is not disclosed.
  • the flow guides shown schematically are technically feasible in modern internal combustion engines only with increased effort.
  • the coolant pump impeller is formed integrally with the side channel pump impeller and the side channel is formed in a first housing part on which the control slide is slidably guided, the axial length required is considerably shortened.
  • the first housing part takes over both the function as a flow housing and as a storage for the slide, so that short pressure channels can be realized.
  • the blades of the side channel pump impeller are formed on a back side of the coolant pump impeller formed as a radial pump impeller and are arranged axially opposite to a side channel.
  • the purely axial alignment of the side channel to the blading reduces the required radial space, since no radially outer overflow channel is needed. Accordingly, a maximum pressure can be generated to the available space.
  • a radially outer boundary wall of the side channel extends axially in the direction of the coolant pump impeller, surrounds the side channel pump impeller radially and is surrounded radially by a radially outer peripheral wall of the control slide.
  • This wall fills the gap between the spool and the rotating side channel pump impeller, and thus between the pressure generating refrigerant flow and the main pump flow.
  • this wall can be used as a guide for the control slide.
  • the first pressure chamber is formed on the axial side facing away from the coolant pump impeller of the control slide and the first housing part defines a second pressure chamber to a first axial side and the control slide to the opposite axial side.
  • the adjustment of the control slide can accordingly completely done by hydraulic forces that are supplied only to the corresponding pressure chambers. Additional annular spaces or piston chambers need not be formed.
  • the fluidic connection to the pressure chambers can be made due to the limitation by the first housing part via a simple bore in this housing part, so that additional lines are not required.
  • the annular projection of the first housing part bounds the two pressure chambers radially inward. Additional seals in this area are not required accordingly. Furthermore, there is a smooth gap-free sliding surface.
  • the pressure channel extends through the annular projection of the first housing part, so that no further lines are to be mounted here, but also the first pressure chamber can be connected directly via the bores in the housing fluidly connected to the side channel of the pump.
  • the pressure channel extends from the outlet of the side channel pump through the first housing part and a second housing part in the first pressure chamber, wherein formed in the second housing part of the valve controlled flow cross-section.
  • the control valve in the housing can also be arranged accordingly, so that here additional connections to the valve omitted.
  • the annular projection of the first housing part at its axial end on a shoulder, from which an annular projection of reduced diameter further extends axially into a corresponding receiving opening of the second housing part, on which the first housing part is fixed. It exists accordingly over the inner projection a direct centering of the two housing parts to each other, whereby the recording and management of the control slide is improved. This can be manufactured with small tolerances, so that a high tightness along the slide with good double-sided leadership is achievable.
  • a particularly simple and releasable attachment results when the first housing part is fastened by means of screws on the second housing part.
  • a connecting channel is formed in the first housing part, which extends from the side channel through the first housing part in the second pressure chamber. This can be made by a short bore or directly during casting. Any additional lines are eliminated and the assembly is facilitated accordingly.
  • the coolant pump according to the invention is simple and inexpensive to manufacture and assemble.
  • the coolant pump consists of an outer housing 10, in which a spiral conveying channel 12 is formed, in which via a likewise formed in the outer housing 10 axial pump inlet 14, a coolant is sucked, which via the delivery channel 12 to a formed in the outer housing 10 tangential pump outlet 16 and is conveyed into a cooling circuit of the internal combustion engine.
  • This outer housing 10 may in particular be formed by a cylinder crankcase, which has a recess for receiving the remaining coolant pump.
  • 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.
  • the pulley 24 is supported by a double row ball bearing 26.
  • a drive via a chain drive would also be possible.
  • a control slide 28 is used, which is displaceable into an annular gap 30 between an outlet 32 of the coolant pump impeller 20 and the surrounding delivery channel 12 and regulates according to the available flow cross section.
  • the control slide 28 is slidably mounted via an inner, hollow cylindrical peripheral wall 34 on a machined outer surface 36 of an annular, axially extending projection 38 of a first inner housing part 40.
  • This inner peripheral wall 34 extends from a bottom 42 of the control slide 28 concentric with a radially outer peripheral wall 44, which also extends in the same direction from the bottom 42 and is displaced into the annular gap 30 for flow control.
  • a bykanalpumpenankratrad 46 is formed, which is driven in accordance with the coolant pump impeller 20.
  • This iskanalpumpencroftrad 46 has blades 48 which are arranged axially opposite to a side channel 50 which is formed in the first inner housing part 40, from which also in the radially inner region of the annular projection 38 for supporting the control slide 28 to the coolant pump impeller 20 opposite side extends axially.
  • an inlet 52 and an outlet 54 are formed, so that the side channel pump impeller 46 with the axially opposite side channel 50 forms a side channel pump 56, via which the pressure of the coolant from the inlet 52 to the outlet 54 of the side channel pump 56 is increased.
  • the hydraulic pressure provided by the side channel pump 56 can now either be supplied to a first pressure chamber 58 which is formed on the side of the control slide 28 facing away from the coolant pump impeller 20 between the bottom 42 of the control slide 28 and a connection surface 60 of a second housing part 62 or one second pressure chamber 64 are fed, between the Bottom 42 of the control slide 28 and the first housing part 40 is arranged.
  • a receptacle 65 for a valve 66 is arranged in the second housing part 62, which is designed as a 3/2-way solenoid valve and a connection to the pressure chambers 58, 64 has, so that depending on the position of its closing body 68, a flow cross-section 70 of a pressure channel 72 is controlled.
  • This pressure channel 72 extends from the outlet 54 of the side channel 50 of the side channel pump 56 first into a radially inner region of the first housing part 40, which forms the annular projection 38 and from there axially into the second housing part 62, in which the controllable flow cross section 70 of the pressure channel 72nd is formed, which is closed by the closing body 68 of the solenoid valve 66 and releasable. From this controllable flow cross-section 70, the pressure channel 72 extends further into the first pressure chamber 58.
  • the second pressure chamber 64 is connected via a connecting channel 74, which is formed in the first housing part 40, with the side channel 50, said connecting channel 74 formed by a bore is that extends from a portion of the inlet 52 from the side channel 50 directly into the second pressure chamber 64.
  • a third, not shown, flow connection of the solenoid valve 66 leads to the suction side of the coolant pump.
  • the annular gap 30 at the outlet 32 of the coolant pump impeller 20 is fully released by the solenoid valve 66 is energized, whereby the closing body 68 is displaced due to a spring force in its the flow cross-section 70 of the pressure channel 72 occlusive position ,
  • the flow port of the solenoid valve 66 which is released in this state, can flow to the pump inlet 14 of the coolant pump.
  • the side channel pump 56 promotes against the closed flow cross-section 70 of the pressure channel 72, whereby an increased pressure builds up in the entire side channel 50, which also acts in the region of the inlet 52 of the side channel 56 and accordingly in the second pressure chamber via the connecting channel 74 64 builds.
  • This increased pressure in the second pressure chamber 64 has the result that at the bottom 42 of the control slide 28, a pressure difference arises, which causes the control slide 28 is displaced in its annular gap 30 releasing position and thus a maximum delivery of the coolant pump is ensured.
  • Too much increase in the pressure in the second pressure chamber 64 is inter alia by leakage through a gap 76 between a side channel 50 radially outwardly delimiting boundary wall 78 of the first housing part 40, which surrounds the sokanalpumpenank 46 immediately, and the radially outer peripheral wall 44 of Control slide 28 avoided, so that the additionally funded by the side channel pump 56 coolant is also used for promotion in the cooling circuit.
  • the coolant from the first pressure chamber 58 can flow off via a return channel, not shown, extending from the solenoid valve 66 through the second housing part 62 and then along the drive shaft 18 in the interior of the first housing part 40th extends and leads via a bore in the coolant pump impeller 20 to the pump inlet 14 of the coolant pump.
  • the solenoid valve 66 is energized, whereby the closing body 68 releases the flow area 70 of the pressure channel 72 and the flow area between the first pressure chamber 58 and the not shown Return channel reduces or closes. Accordingly, the pressure arising at the outlet 54 of the side channel pump 56 is also supplied through the pressure channel 72 to the first pressure chamber 58, while at the same time the pressure in the second pressure chamber 64 decreases, since in the region of the inlet 52 by the suction of the coolant, a reduced pressure. In this case, the coolant present in the second pressure chamber 64 is initially aspirated.
  • valve 66 it is also possible to drive the valve 66 in intermediate positions, whereby for each position of the Regulating slide 28 a balance of forces can be achieved, so that a complete control of the flow cross-section of the annular gap 30 is made possible.
  • the first housing part 40 is attached directly to the second housing part 62. This is done by the first housing part 40 is pushed with an annular projection 80 which extends from the annular projection 38 farther in the coolant pump impeller farther end remote in a radially inner receiving opening 82 of the second housing part 62 until the first housing part 40 with his trained between the projections 38, 80 paragraph 84 abuts against the pad 60 of the second housing part 62. In this position, the first housing part 40 is fastened by means of screws 86 on the second housing part. For this purpose, a plurality of through holes 88 and in the second housing part opposite threaded blind holes 90 are formed in the first housing part.
  • the outer housing 10 For attachment of the two housing parts 40, 62 on the outer housing 10 and consequent to the arrangement of the control slide 28 in the outer housing 10, the outer housing 10 at its pump inlet 14 opposite axial end an opening 92 into which an annular projection 94 of the second housing part 62 such protrudes that the projection 94 abuts against the inner wall of the opening 92.
  • an axial groove 96 Radial outside of this hollow cylindrical projection 94 an axial groove 96 is formed, in which a sealing ring 98 is arranged, which in the attachment of the second housing part 62 on the outer housing 10th is pressed accordingly, the second housing part 62 abuts with its connection surface 60 against an outer wall 100 of the outer housing 10.
  • This projection 94 also serves as a rear stop 102 for the control slide 28, the outer peripheral wall 44 continues with its pointing to the coolant pump impeller 44 end with a slightly larger diameter.
  • a radial groove 104, 106 is formed in each of which a piston ring 108, 110 is arranged, via which the control slide 28 in the radially inner region on the projection 38 of the first housing part 26 and in the radial outer region is slidably supported on an inner wall of the projecting into the opening 92 of the outer housing 10 hollow cylindrical projection 94 of the second housing part 62 and guided sealingly.
  • the coolant pump described is extremely compact, but easy and inexpensive to manufacture and assemble, since a small number of parts is present.
  • On additional lines for hydraulic connection of the side channel 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.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Description

Die Erfindung betrifft eine Kühlmittelpumpe für eine Verbrennungskraftmaschine mit einer Antriebswelle, einem Kühlmittelpumpenlaufrad, welches zumindest drehfest auf der Antriebswelle angeordnet ist und über welches Kühlmittel in einen das Kühlmittelpumpenlaufrad umgebenden Förderkanal förderbar ist, einem verstellbaren Regelschieber, über den ein Durchströmungsquerschnitt eines Ringspalts zwischen einem Austritt des Kühlmittelpumpenlaufrades und dem Förderkanal regelbar ist, einer Seitenkanalpumpe mit einem Seitenkanalpumpenlaufrad, welches auf der Antriebswelle zumindest drehfest angeordnet ist, einem Seitenkanal der Seitenkanalpumpe, in dem durch Drehung des Seitenkanalpumpenlaufrades ein Druck erzeugbar ist, einem Druckkanal, über welchen ein Auslass des Seitenkanals mit einem ersten Druckraum des Regelschiebers fluidisch verbindbar ist, und einem Ventil, über welches ein Durchströmungsquerschnitt des Druckkanals verschließbar und freigebbar ist.The invention relates to a coolant pump for an internal combustion engine with a drive shaft, a coolant pump impeller, which is at least rotationally fixed on the drive shaft and via which coolant in a surrounding the coolant pump impeller conveyor is conveyed, an adjustable control slide, via which a flow cross section of an annular gap between an outlet of the Kühlmittelpumpenlaufrades and the delivery channel is controllable, a side channel pump with a Seitenkanalpumpenlaufrad which is rotatably mounted on the drive shaft, a side channel of the side channel pump in which by rotation of the Seitenkanalpumpenlaufrades a pressure can be generated, a pressure channel through which an outlet of the side channel with a first Pressure chamber of the control slide is fluidically connectable, and a valve, via which a flow cross-section of the pressure channel can be closed and released.

Derartige 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 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, especially the cold running phase of the engine should be shortened. This is done, inter alia, by throttling or completely shutting off the coolant flow 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 to compress other hydraulic fluids for actuation, are mechanically controllable Coolant pumps have become known, on the drive shaft, a second delivery wheel is arranged, via which the pressure for adjusting the slide is provided. These pumps are designed, for example, as side channel pumps or servo pumps.

Eine derartige Kühlmitteleinrichtung mit einer als Sekundärpumpe wirkenden Seitenkanalpumpe ist aus der DE 10 2012 207 387 A1 bekannt. Bei dieser Pumpe befindet sich an der Rückseite der Pumpe ein Schieber, welcher über einen Druck in einer Ringkammer verschiebbar ist und über eine Feder zurückgestellt werden kann. Diese Ringkammer ist in einem Gehäuse ausgebildet, welches wiederum an der Rückseite des Schiebers angeordnet ist und in dem auch ein erster Seitenkanal der Seitenkanalpumpe angeordnet ist, der entsprechend gegenüberliegend zum auf der Welle angeordneten Seitenkanalpumpenlaufrad angeordnet ist. An der zum Seitenkanalpumpenlaufrad gegenüberliegenden Seite ist ein zweiter Seitenkanal in einem weiteren Gehäuseteil ausgebildet. Über ein 3/2-Wegeventil wird bei dieser Pumpe in einer ersten Stellung eine Druckseite der Seitenkanalpumpe verschlossen und eine Saugseite der Pumpe mit dem Kühlkreislauf und dem Schieber verbunden und in einer zweiten Stellung die Druckseite mit der Ringkammer des Schiebers und die Saugseite mit dem Kühlkreislauf verbunden. Eine detaillierte Kanal- und Strömungsführung wird nicht offenbart. Die schematisch dargestellten Strömungsführungen sind in modernen Verbrennungsmotoren technisch nur mit erhöhtem Aufwand realisierbar. Zusätzlich bestehen ein erhöhter Montageaufwand und vor allem ein erhöhter Bauraumbedarf sowohl für die schematisch dargestellten Strömungsführungen als auch aufgrund der gewählten Anordnungen und Gehäuseteilungen, so dass eine derartige Pumpe nicht in einer entsprechende Anordnung eines Zylinderkurbelgehäuse angeordnet und montiert werden könnte.Such a coolant device with a secondary pump acting as a secondary pump is from the DE 10 2012 207 387 A1 known. This pump is located at the back of the pump, a slider which is displaceable by a pressure in an annular chamber and can be reset by a spring. This annular chamber is formed in a housing, which in turn is arranged on the back of the slide and in which a first side channel of the side channel pump is arranged, which is arranged correspondingly opposite to the arranged on the shaft side channel pump impeller. On the side opposite the side channel pump impeller, a second side channel is formed in a further housing part. About a 3/2-way valve, a pressure side of the side channel pump is closed in this pump in a first position and a suction side of the pump connected to the cooling circuit and the slider and in a second position, the pressure side with the annular chamber of the slide and the suction side with the cooling circuit connected. A detailed channel and flow guidance is not disclosed. The flow guides shown schematically are technically feasible in modern internal combustion engines only with increased effort. In addition, there is an increased installation effort and especially an increased space requirement for both the flow guides shown schematically as well as due to the selected arrangements and housing divisions, so that such a pump could not be arranged and mounted in a corresponding arrangement of a cylinder crankcase.

Zusätzlich ist aus der US 2014/050562 A1 eine mechanisch regelbare Kühlmittelpumpe bekannt, auf deren Welle zusätzlich zum Pumpenlaufrad ein Seitenkanallaufrad angeordnet ist, über welches ein Druck zur Verstellung des Regelschiebers erzeugt wird. Dieser Druck ist über ein Ventil entweder abführbar oder einer Rückseite eines Kolbens zuführbar, der mit dem Regelschieber verbunden ist, so dass dieser den Regelschieber über das Laufrad der Kühlmittelpumpe schiebt.In addition is from the US 2014/050562 A1 a mechanically controllable coolant pump known, on the shaft in addition to the pump impeller a Seitenkanallaufrad is arranged, via which a pressure for adjusting the control slide is generated. This pressure can either be dissipated via a valve or fed to a rear side of a piston which is connected to the control slide so that it pushes the control slide over the impeller of the coolant pump.

Es stellt sich daher die Aufgabe, eine Kühlmittelpumpe für eine Verbrennungskraftmaschine zu schaffen, bei der der Montageaufwand und der benötigte Bauraum deutlich reduziert werden. Insbesondere soll die axiale Baulänge verkürzt werden und möglichst keine zusätzlichen Leitungsmontagen erforderlich sein, so dass ein Einbau als Steckpumpe in eine entsprechende axial kurze Ausnehmung eines Kurbelgehäuse ermöglicht wird.It is therefore the object to provide a coolant pump for an internal combustion engine, in which the assembly costs and the required space can be significantly reduced. In particular, the axial length should be shortened and possible no additional line assemblies are required so that installation as a plug-in pump in a corresponding axially short recess of a crankcase is made possible.

Diese Aufgabe wird durch eine Kühlmittelpumpe mit den Merkmalen des Hauptanspruchs 1 gelöst.This object is achieved by a coolant pump with the features of the main claim 1.

Dadurch, dass das Kühlmittelpumpenlaufrad einstückig mit dem Seitenkanalpumpenlaufrad ausgebildet ist und der Seitenkanal in einem ersten Gehäuseteil ausgebildet ist, auf dem der Regelschieber gleitend geführt ist, wird die axial benötigte Baulänge erheblich verkürzt. Zusätzlich entfallen Montageschritte zur Befestigung des Laufrades auf der Welle. Auch entfällt die Herstellung eines Bauteils. Das erste Gehäuseteil übernimmt sowohl die Funktion als Strömungsgehäuse als auch als Lagerung für den Schieber, so dass kurze Druckkanäle realisierbar sind.Characterized in that the coolant pump impeller is formed integrally with the side channel pump impeller and the side channel is formed in a first housing part on which the control slide is slidably guided, the axial length required is considerably shortened. In addition, there are no installation steps for mounting the impeller on the shaft. Also eliminates the production of a component. The first housing part takes over both the function as a flow housing and as a storage for the slide, so that short pressure channels can be realized.

Vorzugsweise sind die Schaufeln des Seitenkanalpumpenlaufrades auf einer Rückseite des als Radialpumpenlaufrad ausgebildeten Kühlmittelpumpenlaufrades ausgebildet und sind einem Seitenkanal axial gegenüberliegend angeordnet. Die rein axiale Ausrichtung des Seitenkanals zur Beschaufelung verringert den benötigten radialen Bauraum, da kein radial äußerer Überströmungskanal benötigt wird. Entsprechend kann zum vorhandenen Bauraum ein maximaler Druck erzeugt werden.Preferably, the blades of the side channel pump impeller are formed on a back side of the coolant pump impeller formed as a radial pump impeller and are arranged axially opposite to a side channel. The purely axial alignment of the side channel to the blading reduces the required radial space, since no radially outer overflow channel is needed. Accordingly, a maximum pressure can be generated to the available space.

In einer vorteilhaften Ausführung der Erfindung erstreckt sich eine radial äußere Begrenzungswand des Seitenkanals axial in Richtung des Kühlmittelpumpenlaufrades, umgibt das Seitenkanalpumpenlaufrad radial und ist radial von einer radial äußeren Umfangswand des Regelschiebers umgeben. Diese Wand füllt entsprechend den Spalt zwischen dem Schieber und dem sich drehenden Seitenkanalpumpenlaufrad und somit zwischen dem Druck erzeugenden Kühlmittelstrom und dem Förderstrom der Hauptpumpe. Zusätzlich kann diese Wand als Führung für den Regelschieber genutzt werden.In an advantageous embodiment of the invention, a radially outer boundary wall of the side channel extends axially in the direction of the coolant pump impeller, surrounds the side channel pump impeller radially and is surrounded radially by a radially outer peripheral wall of the control slide. This wall fills the gap between the spool and the rotating side channel pump impeller, and thus between the pressure generating refrigerant flow and the main pump flow. In addition, this wall can be used as a guide for the control slide.

Besonders vorteilhaft ist es, wenn der Regelschieber auf einer Außenfläche eines ringförmigen, sich axial erstreckenden Vorsprungs des ersten Gehäuseteils gleitend geführt ist. Dieser Vorsprung ist entsprechend im radial inneren Bereich des ersten Gehäuseteils ausgebildet und ermöglicht entsprechend eine innere Lagerung des Regelschiebers auf der vorteilhafterweise maschinell bearbeiteten Außenfläche. Diese innere Lagerung des Regelschiebers vereinfacht den Einbau in eine Aufnahmeöffnung eines Zylinderkurbelgehäuses, deren Innenflächen dann nicht bearbeitet werden müssen. Des Weiteren bewirkt eine solche innere Führung eine sehr exakte axiale Bewegung, ohne dass ein Verkanten oder Kippen des Regelschiebers zu befürchten ist, da immer eine ausreichend lange Führungsfläche trotz des geringen verwendeten Bauraums zur Verfügung steht.It when the control slide is slidably guided on an outer surface of an annular, axially extending projection of the first housing part is particularly advantageous. This projection is correspondingly formed in the radially inner region of the first housing part and correspondingly allows an inner bearing of the control slide on the advantageously machined outer surface. This inner bearing of the control slide simplifies installation in a receiving opening of a cylinder crankcase, the inner surfaces then do not need to be edited. Furthermore, such an inner guide causes a very exact axial movement, without jerking or tilting of the control slide is to be feared, as always a sufficiently long guide surface is available despite the low space used.

Vorzugsweise ist der erste Druckraum an der vom Kühlmittelpumpenlaufrad abgewandten axialen Seite des Regelschiebers ausgebildet und das erste Gehäuseteil begrenzt einen zweiten Druckraum zu einer ersten axialen Seite und der Regelschieber zur entgegengesetzten axialen Seite. Die Verstellung des Regelschiebers kann entsprechend vollständig über hydraulische Kräfte erfolgen, die lediglich den entsprechenden Druckräumen zugeführt werden. Zusätzliche Ringräume oder Kolbenräume müssen nicht ausgebildet werden. Die fluidische Verbindung zu den Druckräumen kann aufgrund der Begrenzung durch das erste Gehäuseteil über eine einfache Bohrung in diesem Gehäuseteil hergestellt werden, so dass zusätzliche Leitungen nicht erforderlich sind.Preferably, the first pressure chamber is formed on the axial side facing away from the coolant pump impeller of the control slide and the first housing part defines a second pressure chamber to a first axial side and the control slide to the opposite axial side. The adjustment of the control slide can accordingly completely done by hydraulic forces that are supplied only to the corresponding pressure chambers. Additional annular spaces or piston chambers need not be formed. The fluidic connection to the pressure chambers can be made due to the limitation by the first housing part via a simple bore in this housing part, so that additional lines are not required.

In bevorzugter Weise begrenzt der ringförmige Vorsprung des ersten Gehäuseteils die beiden Druckräume nach radial innen. Zusätzliche Abdichtungen in diesem Bereich sind entsprechend nicht erforderlich. Des Weiteren ergibt sich eine glatte spaltfreie Gleitfläche.Preferably, the annular projection of the first housing part bounds the two pressure chambers radially inward. Additional seals in this area are not required accordingly. Furthermore, there is a smooth gap-free sliding surface.

In einer bevorzugten Ausführung erstreckt sich der Druckkanal durch den ringförmigen Vorsprung des ersten Gehäuseteils, so dass auch hier keine weiteren Leitungen zu montieren sind, sondern auch der erste Druckraum direkt über die Bohrungen im Gehäuse fluidisch mit dem Seitenkanal der Pumpe verbunden werden kann.In a preferred embodiment, the pressure channel extends through the annular projection of the first housing part, so that no further lines are to be mounted here, but also the first pressure chamber can be connected directly via the bores in the housing fluidly connected to the side channel of the pump.

Vorteilhafterweise erstreckt sich der Druckkanal vom Auslass der Seitenkanalpumpe durch das erste Gehäuseteil und ein zweites Gehäuseteil in den ersten Druckraum, wobei im zweiten Gehäuseteil der vom Ventil beherrschte Durchströmungsquerschnitt ausgebildet ist. Neben der vollständigen Ausbildung der Verbindungs- und Druckkanäle zur Steuerung des Regelschiebers kann entsprechend auch das Regelventil im Gehäuse angeordnet werden, so dass auch hier zusätzliche Verbindungen zum Ventil entfallen.Advantageously, the pressure channel extends from the outlet of the side channel pump through the first housing part and a second housing part in the first pressure chamber, wherein formed in the second housing part of the valve controlled flow cross-section. In addition to the complete design of the connection and pressure channels for controlling the control slide, the control valve in the housing can also be arranged accordingly, so that here additional connections to the valve omitted.

Vorzugsweise weist der ringförmige Vorsprung des ersten Gehäuseteils an seinem axialen Ende einen Absatz auf, von dem aus sich ein ringförmiger Vorsprung mit verringertem Durchmesser weiter axial in eine entsprechende Aufnahmeöffnung des zweiten Gehäuseteils erstreckt, an dem das erste Gehäuseteil befestigt ist. Es besteht entsprechend über den inneren Vorsprung eine unmittelbare Zentrierung der beiden Gehäuseteile zueinander, wodurch die Aufnahme und Führung des Regelschiebers verbessert wird. Dieser kann mit geringen Toleranzen gefertigt werden, so dass eine hohe Dichtigkeit entlang des Schiebers bei guter beidseitiger Führung erreichbar ist.Preferably, the annular projection of the first housing part at its axial end on a shoulder, from which an annular projection of reduced diameter further extends axially into a corresponding receiving opening of the second housing part, on which the first housing part is fixed. It exists accordingly over the inner projection a direct centering of the two housing parts to each other, whereby the recording and management of the control slide is improved. This can be manufactured with small tolerances, so that a high tightness along the slide with good double-sided leadership is achievable.

Eine besonders einfache und lösbare Befestigung ergibt sich, wenn das erste Gehäuseteil mittels Schrauben am zweiten Gehäuseteil befestigt ist.A particularly simple and releasable attachment results when the first housing part is fastened by means of screws on the second housing part.

In einer besonders bevorzugten Ausführung der Erfindung ist im ersten Gehäuseteil ein Verbindungskanal ausgebildet, der sich vom Seitenkanal durch das erste Gehäuseteil in den zweiten Druckraum erstreckt. Dieser kann durch eine kurze Bohrung oder direkt beim Gießen hergestellt werden. Jegliche zusätzliche Leitungen entfallen und die Montage wird entsprechend erleichtert.In a particularly preferred embodiment of the invention, a connecting channel is formed in the first housing part, which extends from the side channel through the first housing part in the second pressure chamber. This can be made by a short bore or directly during casting. Any additional lines are eliminated and the assembly is facilitated accordingly.

Es wird somit eine Kühlmittelpumpe für eine Verbrennungskraftmaschine geschaffen, bei der aufgrund der axialen Anordnung der Einzelteile zueinander ein deutlich reduzierter axialer Bauraum benötigt wird. Die Pumpe ist einfach zu montieren, da zusätzliche Leitungen entfallen und weniger Bauteile verwendet werden müssen. Die Pumpe weist eine hohe Zuverlässigkeit auf, da der Schieber eine zuverlässige Führung und Lagerung aufweist. Entsprechend ist die erfindungsgemäße Kühlmittelpumpe einfach und kostengünstig herstellbar und montierbar.It is thus created a coolant pump for an internal combustion engine, in which due to the axial arrangement of the individual parts to each other a significantly reduced axial space is needed. The pump is easy to assemble, eliminating the need for extra lines and fewer components. The pump has a high reliability because the slider has a reliable guidance and storage. Accordingly, the coolant pump according to the invention is simple and inexpensive to manufacture and assemble.

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

  • Figur 1 zeigt eine Seitenansicht einer erfindungsgemäßen Kühlmittelpumpe in geschnittener Darstellung.
  • Figur 2 zeigt eine zu Figur 1 gedrehte Seitenansicht der erfindungsgemäßen Kühlmittelpumpe 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 according to the invention in a sectional view.
  • FIG. 2 shows one too FIG. 1 rotated side view of the coolant pump according to the invention in a sectional view.

Die erfindungsgemäße 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, welches über den Förderkanal 12 zu einem im Außengehäuse 10 ausgebildeten tangentialen Pumpenauslass 16 und in einen Kühlkreislauf der Verbrennungskraftmaschine gefördert wird. Dieses Außengehäuse 10 kann insbesondere durch ein Zylinderkurbelgehäuse gebildet sein, welches eine Ausnehmung zur Aufnahme der übrigen Kühlmittelpumpe aufweist.The coolant pump according to the invention consists of an outer housing 10, in which a spiral conveying channel 12 is formed, in which via a likewise formed in the outer housing 10 axial pump inlet 14, a coolant is sucked, which via the delivery channel 12 to a formed in the outer housing 10 tangential pump outlet 16 and is conveyed into a cooling circuit of the internal combustion engine. This outer housing 10 may in particular be formed by a cylinder crankcase, which has a recess for receiving the remaining coolant pump.

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.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.

Der Antrieb des Kühlmittelpumpenlaufrades 20 erfolgt über einen Riemen 22, der ein Riemenrad 24 antriebt, welches am zum Kühlmittelpumpenlaufrad 20 entgegengesetzten axialen Ende der Antriebswelle 18 befestigt ist. Das Riemenrad 24 wird über ein zweireihiges Kugellager 26 gelagert. Ein Antrieb über einen Kettentrieb wäre ebenfalls möglich.The drive of the coolant pump impeller 20 via a belt 22 which drives 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. A drive via a chain drive would also be possible.

Um den von der Kühlmittelpumpe geförderten Volumenstrom ändern zu können, wird ein Regelschieber 28 verwendet, der in einen Ringspalt 30 zwischen einem Austritt 32 des Kühlmittelpumpenlaufrades 20 und dem umgebenden Förderkanal 12 verschiebbar ist und entsprechend den zur Verfügung stehenden Durchströmungsquerschnitt regelt.In order to be able to change the volume flow conveyed by the coolant pump, a control slide 28 is used, which is displaceable into an annular gap 30 between an outlet 32 of the coolant pump impeller 20 and the surrounding delivery channel 12 and regulates according to the available flow cross section.

Der Regelschieber 28 ist über eine innere, hohlzylindrische Umfangswand 34 auf einer mechanisch bearbeiteten Außenfläche 36 eines ringförmigen, sich axial erstreckenden Vorsprungs 38 eines ersten inneren Gehäuseteils 40 gleitend gelagert. Diese innere Umfangswand 34 erstreckt sich von einem Boden 42 des Regelschiebers 28 konzentrisch zu einer radial äußeren Umfangswand 44, welche sich in gleicher Richtung ebenfalls vom Boden 42 erstreckt und in den Ringspalt 30 zur Volumenstromregelung verschoben wird.The control slide 28 is slidably mounted via an inner, hollow cylindrical peripheral wall 34 on a machined outer surface 36 of an annular, axially extending projection 38 of a first inner housing part 40. This inner peripheral wall 34 extends from a bottom 42 of the control slide 28 concentric with a radially outer peripheral wall 44, which also extends in the same direction from the bottom 42 and is displaced into the annular gap 30 for flow control.

Um diesen Regelschieber 28 betätigen zu können, ist erfindungsgemäß an der zum Pumpeneinlass 14 entgegengesetzten axialen Seite des Kühlmittelpumpenlaufrades 20 einteilig mit dem Kühlmittelpumpenlaufrad 20 ein Seitenkanalpumpenlaufrad 46 ausgebildet, welches entsprechend mit dem Kühlmittelpumpenlaufrad 20 angetrieben wird. Dieses Seitenkanalpumpenlaufrad 46 weist Schaufeln 48 auf, die axial gegenüberliegend zu einem als Seitenkanal 50 angeordnet sind, der in dem ersten inneren Gehäuseteil 40 ausgebildet ist, von dem aus sich auch im radial innenliegenden Bereich der ringförmige Vorsprung 38 zur Lagerung des Regelschiebers 28 zur vom Kühlmittelpumpenlaufrad 20 abgewandten Seite axial erstreckt. In diesem ersten Gehäuseteil 40 sind ein Einlass 52 und ein Auslass 54 ausgebildet, so dass das Seitenkanalpumpenlaufrad 46 mit dem axial gegenüberliegenden Seitenkanal 50 eine Seitenkanalpumpe 56 bildet, über welche der Druck des Kühlmittels vom Einlass 52 zum Auslass 54 der Seitenkanalpumpe 56 erhöht wird.In order to operate this control slide 28, according to the invention at the pump inlet 14 opposite axial side of the coolant pump impeller 20 integral with the coolant pump impeller 20 a Seitenkanalpumpenlaufrad 46 is formed, which is driven in accordance with the coolant pump impeller 20. This Seitenkanalpumpenlaufrad 46 has blades 48 which are arranged axially opposite to a side channel 50 which is formed in the first inner housing part 40, from which also in the radially inner region of the annular projection 38 for supporting the control slide 28 to the coolant pump impeller 20 opposite side extends axially. In this first housing part 40, an inlet 52 and an outlet 54 are formed, so that the side channel pump impeller 46 with the axially opposite side channel 50 forms a side channel pump 56, via which the pressure of the coolant from the inlet 52 to the outlet 54 of the side channel pump 56 is increased.

Der durch die Seitenkanalpumpe 56 zur Verfügung gestellte hydraulische Druck kann nun entweder einem ersten Druckraum 58 zugeführt werden, der an der vom Kühlmittelpumpenlaufrad 20 abgewandten Seite des Regelschiebers 28 zwischen dem Boden 42 des Regelschiebers 28 und einer Anschlussfläche 60 eines zweiten Gehäuseteils 62 ausgebildet ist oder einem zweiten Druckraum 64 zugeführt werden, der zwischen dem Boden 42 des Regelschiebers 28 und dem ersten Gehäuseteil 40 angeordnet ist. Um den Druck der Seitenkanalpumpe 56 diesen Druckräumen 58, 64 gezielt zuführen zu können, ist im zweiten Gehäuseteil 62 eine Aufnahme 65 für ein Ventil 66 angeordnet, welches als 3/2-Wege-Magnetventil ausgebildet ist und eine Verbindung zu den Druckräumen 58, 64 aufweist, so dass je nach Position seines Schließkörpers 68 ein Durchströmungsquerschnitt 70 eines Druckkanals 72 geregelt wird.The hydraulic pressure provided by the side channel pump 56 can now either be supplied to a first pressure chamber 58 which is formed on the side of the control slide 28 facing away from the coolant pump impeller 20 between the bottom 42 of the control slide 28 and a connection surface 60 of a second housing part 62 or one second pressure chamber 64 are fed, between the Bottom 42 of the control slide 28 and the first housing part 40 is arranged. In order to selectively supply the pressure of the side channel pump 56 to these pressure chambers 58, 64, a receptacle 65 for a valve 66 is arranged in the second housing part 62, which is designed as a 3/2-way solenoid valve and a connection to the pressure chambers 58, 64 has, so that depending on the position of its closing body 68, a flow cross-section 70 of a pressure channel 72 is controlled.

Dieser Druckkanal 72 erstreckt sich vom Auslass 54 des Seitenkanals 50 der Seitenkanalpumpe 56 zunächst in einen radial inneren Bereich des ersten Gehäuseteils 40, der den ringförmigen Vorsprung 38 bildet und von dort axial in das zweite Gehäuseteil 62, in dem der regelbare Durchströmungsquerschnitt 70 des Druckkanals 72 ausgebildet ist, der durch den Schließkörper 68 des Magnetventils 66 verschließbar und freigebbar ist. Von diesem regelbaren Durchströmungsquerschnitt 70 erstreckt sich der Druckkanal 72 weiter bis in den ersten Druckraum 58. Der zweite Druckraum 64 ist über einen Verbindungskanal 74, welcher im ersten Gehäuseteil 40 ausgebildet ist, mit dem Seitenkanal 50 verbunden, wobei dieser Verbindungskanal 74 durch eine Bohrung gebildet ist, die sich von einem Bereich des Einlasses 52 aus dem Seitenkanal 50 direkt in den zweiten Druckraum 64 erstreckt. Ein dritter, nicht dargestellter Strömungsanschluss des Magnetventils 66 führt zur Saugseite der Kühlmittelpumpe.This pressure channel 72 extends from the outlet 54 of the side channel 50 of the side channel pump 56 first into a radially inner region of the first housing part 40, which forms the annular projection 38 and from there axially into the second housing part 62, in which the controllable flow cross section 70 of the pressure channel 72nd is formed, which is closed by the closing body 68 of the solenoid valve 66 and releasable. From this controllable flow cross-section 70, the pressure channel 72 extends further into the first pressure chamber 58. The second pressure chamber 64 is connected via a connecting channel 74, which is formed in the first housing part 40, with the side channel 50, said connecting channel 74 formed by a bore is that extends from a portion of the inlet 52 from the side channel 50 directly into the second pressure chamber 64. A third, not shown, flow connection of the solenoid valve 66 leads to the suction side of the coolant pump.

Soll die Kühlmittelpumpe im Betrieb eine maximale Kühlmittelmenge fördern, wird der Ringspalt 30 am Austritt 32 des Kühlmittelpumpenlaufrades 20 vollständig freigegeben, indem das Magnetventil 66 nicht bestromt wird, wodurch der Schließkörper 68 aufgrund einer Federkraft in seine den Durchströmungsquerschnitt 70 des Druckkanals 72 verschließende Stellung verschoben wird. Dies hat zur Folge, dass im ersten Druckraum 58 kein Druck durch das Kühlmittel aufgebaut wird, sondern das im Druckraum 58 vorhandene Kühlmittel über den nicht dargestellten anderen Strömungsanschluss des Magnetventils 66, der in diesem Zustand freigegeben ist, zum Pumpeneinlass 14 der Kühlmittelpumpe abströmen kann. Stattdessen fördert in diesem Zustand die Seitenkanalpumpe 56 gegen den geschlossenen Durchströmungsquerschnitt 70 des Druckkanals 72, wodurch sich im gesamten Seitenkanal 50 ein erhöhter Druck aufbaut, der auch im Bereich des Einlasses 52 der Seitenkanalpumpe 56 wirkt und sich entsprechend über den Verbindungskanal 74 auch im zweiten Druckraum 64 aufbaut. Dieser erhöhte Druck im zweiten Druckraum 64 hat zur Folge, dass am Boden 42 des Regelschiebers 28 eine Druckdifferenz entsteht, die dazu führt, dass der Regelschieber 28 in seine den Ringspalt 30 freigebende Position verschoben wird und somit eine Maximalförderung der Kühlmittelpumpe sichergestellt wird. Bei einem Ausfall der elektrischen Versorgung des Magnetventils 66 nimmt der Regelschieber 28 entsprechend die gleiche Position ein, so dass auch in diesem Notlaufbetriebszustand eine Maximalförderung der Kühlmittelpumpe sichergestellt wird, ohne dass hierzu eine Rückstellfeder oder eine andere, nicht hydraulische Kraft notwendig wäre.If the coolant pump to promote a maximum amount of coolant during operation, the annular gap 30 at the outlet 32 of the coolant pump impeller 20 is fully released by the solenoid valve 66 is energized, whereby the closing body 68 is displaced due to a spring force in its the flow cross-section 70 of the pressure channel 72 occlusive position , This has the consequence that in the first pressure chamber 58 no pressure by the coolant is constructed, but the coolant present in the pressure chamber 58 via the other not shown, the flow port of the solenoid valve 66, which is released in this state, can flow to the pump inlet 14 of the coolant pump. Instead, in this state, the side channel pump 56 promotes against the closed flow cross-section 70 of the pressure channel 72, whereby an increased pressure builds up in the entire side channel 50, which also acts in the region of the inlet 52 of the side channel 56 and accordingly in the second pressure chamber via the connecting channel 74 64 builds. This increased pressure in the second pressure chamber 64 has the result that at the bottom 42 of the control slide 28, a pressure difference arises, which causes the control slide 28 is displaced in its annular gap 30 releasing position and thus a maximum delivery of the coolant pump is ensured. In case of failure of the electrical supply of the solenoid valve 66 of the control slide 28 corresponding to the same position, so that even in this emergency operating mode maximum delivery of the coolant pump 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 64 wird unter anderem durch eine Leckage über einen Spalt 76 zwischen einer den Seitenkanal 50 radial nach außen begrenzenden Begrenzungswand 78 des ersten Gehäuseteils 40, welche das Seitenkanalpumpenlaufrad 46 unmittelbar umgibt, und der radial äußeren Umfangswand 44 des Regelschiebers 28 vermieden, so dass das zusätzlich durch die Seitenkanalpumpe 56 geförderte Kühlmittel ebenfalls zur Förderung in den Kühlkreislauf genutzt wird. Das Kühlmittel aus dem ersten Druckraum 58 kann über einen nicht dargestellten Rückführkanal abfließen, der sich vom Magnetventil 66 durch das zweite Gehäuseteil 62 und anschließend entlang der Antriebswelle 18 im Innern des ersten Gehäuseteils 40 erstreckt und über eine Bohrung im Kühlmittelpumpenlaufrad 20 zum Pumpeneinlass 14 der Kühlmittelpumpe führt.Too much increase in the pressure in the second pressure chamber 64 is inter alia by leakage through a gap 76 between a side channel 50 radially outwardly delimiting boundary wall 78 of the first housing part 40, which surrounds the Seitenkanalpumpenlaufrad 46 immediately, and the radially outer peripheral wall 44 of Control slide 28 avoided, so that the additionally funded by the side channel pump 56 coolant is also used for promotion in the cooling circuit. The coolant from the first pressure chamber 58 can flow off via a return channel, not shown, extending from the solenoid valve 66 through the second housing part 62 and then along the drive shaft 18 in the interior of the first housing part 40th extends and leads via a bore in the coolant pump impeller 20 to the pump inlet 14 of the coolant pump.

Wird ein reduzierter Kühlmittelstrom zum Kühlkreislauf von der Motorsteuerung gefordert, wie dies beispielsweise während der Kaltlaufphase der Fall ist, wird das Magnetventil 66 bestromt, wodurch der Schließkörper 68 den Durchströmungsquerschnitt 70 des Druckkanals 72 freigibt und den Durchströmungsquerschnitt zwischen dem ersten Druckraum 58 und dem nicht dargestellten Rückführkanal reduziert beziehungsweise verschließt. Entsprechend wird der am Auslass 54 der Seitenkanalpumpe 56 entstehende Druck auch durch den Druckkanal 72 dem ersten Druckraum 58 zugeführt, während gleichzeitig der Druck im zweiten Druckraum 64 sinkt, da im Bereich des Einlasses 52 durch das Ansaugen des Kühlmittels ein verringerter Druck entsteht. Dabei wird zunächst auch das im zweiten Druckraum 64 vorhandene Kühlmittel abgesaugt. In diesem Zustand liegt entsprechend eine im Vergleich zur anderen Stellung des Magnetventils 66 entgegengesetzte Druckdifferenz am Boden 42 des Regelschiebers 28 an, die dazu führt, dass der Regelschieber 28 in den Ringspalt 30 verschoben wird und somit der Kühlmittelstrom im Kühlkreislauf unterbrochen wird. Bei erhöhtem Druckaufbau im ersten Druckraum 58 steigt nach einiger Zeit auch der Druck im Seitenkanal 50 und im zweiten Druckraum 64, was jedoch nicht zu einer Rückstellung führt, da die Leckage aus dem zweiten Druckraum 64 größer ist als aus dem ersten Druckraum 58 und zur Verstellung zusätzlich eine Reibungskraft zu überwinden wäre. Des Weiteren ist in diesem Zustand der Druck am Auslass 54 des Seitenkanals 50 immer größer als im Bereich des Verbindungskanals 74. Entsprechend verbleibt der Regelschieber 28 in der gewünschten Position, ohne dass eine zu starke Druckerhöhung entsteht.If a reduced coolant flow to the cooling circuit of the engine control required, as is the case for example during the cold running phase, the solenoid valve 66 is energized, whereby the closing body 68 releases the flow area 70 of the pressure channel 72 and the flow area between the first pressure chamber 58 and the not shown Return channel reduces or closes. Accordingly, the pressure arising at the outlet 54 of the side channel pump 56 is also supplied through the pressure channel 72 to the first pressure chamber 58, while at the same time the pressure in the second pressure chamber 64 decreases, since in the region of the inlet 52 by the suction of the coolant, a reduced pressure. In this case, the coolant present in the second pressure chamber 64 is initially aspirated. In this state, a correspondingly opposite to the other position of the solenoid valve 66 pressure difference at the bottom 42 of the control slide 28, which causes the control slide 28 is moved into the annular gap 30 and thus the coolant flow is interrupted in the cooling circuit. With increased pressure build-up in the first pressure chamber 58, the pressure in the side channel 50 and the second pressure chamber 64 increases after some time, but this does not lead to a provision, since the leakage from the second pressure chamber 64 is greater than from the first pressure chamber 58 and for adjustment In addition, a friction force would be overcome. Furthermore, in this state, the pressure at the outlet 54 of the side channel 50 is always greater than in the region of the connecting channel 74. Accordingly, the control slide 28 remains in the desired position, without causing an excessive pressure increase.

Wird ein regelbares Magnetventil 66 verwendet, ist es auch möglich, das Ventil 66 in Zwischenstellungen zu fahren, wodurch für jede Position des Regelschiebers 28 ein Kräftegleichgewicht erzielbar ist, so dass eine vollständige Regelung des Durchströmungsquerschnitts des Ringspaltes 30 ermöglicht wird.If a controllable solenoid valve 66 is used, it is also possible to drive the valve 66 in intermediate positions, whereby for each position of the Regulating slide 28 a balance of forces can be achieved, so that a complete control of the flow cross-section of the annular gap 30 is made possible.

Um die kompakte Bauweise durch die einteilige Ausführung des Kühlmittelpumpenlaufrades 20 mit dem Seitenkanalpumpenlaufrad 46 und eine dichte Verbindung der im ersten Gehäuseteil 40 und im zweiten Gehäuseteil 62 ausgebildeten Kanalabschnitte des Druckkanals 72 oder des Rückführkanals gewährleisten zu können und die geringe Leckagen über den Regelschieber 28 zu gewährleisten und so eine vollständige Regelbarkeit sicher zu stellen, wird das erste Gehäuseteil 40 direkt am zweiten Gehäuseteil 62 befestigt. Dies erfolgt, indem das erste Gehäuseteil 40 mit einem ringförmigen Vorsprung 80, der sich mit verringertem Durchmesser vom ringförmigen Vorsprung 38 weiter in vom Kühlmittelpumpenlaufrad abgewandten Ende erstreckt, in eine radial innere Aufnahmeöffnung 82 des zweiten Gehäuseteils 62 geschoben wird, bis das erste Gehäuseteil 40 mit seinem zwischen den Vorsprüngen 38, 80 ausgebildeten Absatz 84 gegen die Anschlussfläche 60 des zweiten Gehäuseteils 62 anliegt. In dieser Position wird das erste Gehäuseteil 40 mittels Schrauben 86 am zweiten Gehäuseteil befestigt. Hierzu sind im ersten Gehäuseteil mehrere Durchgangsbohrungen 88 und im zweiten Gehäuseteil gegenüberliegende Gewindesacklöcher 90 ausgebildet.In order to ensure the compact design by the one-piece design of the coolant pump impeller 20 with the Seitenkanalpumpenlaufrad 46 and a tight connection formed in the first housing part 40 and the second housing part 62 channel sections of the pressure channel 72 or the return channel and to ensure the low leakage through the control slide 28 and to ensure complete controllability, the first housing part 40 is attached directly to the second housing part 62. This is done by the first housing part 40 is pushed with an annular projection 80 which extends from the annular projection 38 farther in the coolant pump impeller farther end remote in a radially inner receiving opening 82 of the second housing part 62 until the first housing part 40 with his trained between the projections 38, 80 paragraph 84 abuts against the pad 60 of the second housing part 62. In this position, the first housing part 40 is fastened by means of screws 86 on the second housing part. For this purpose, a plurality of through holes 88 and in the second housing part opposite threaded blind holes 90 are formed in the first housing part.

Zur Befestigung der beiden Gehäuseteile 40, 62 am Außengehäuse 10 und daraus folgende zur Anordnung des Regelschiebers 28 im Außengehäuse 10 weist das Außengehäuse 10 an seinem zum Pumpeneinlass 14 entgegengesetzten axialen Ende eine Öffnung 92 auf, in die ein ringförmiger Vorsprung 94 des zweiten Gehäuseteils 62 derart ragt, dass der Vorsprung 94 gegen die Innenwand der Öffnung 92 anliegt. Radial außerhalb dieses hohlzylindrischen Vorsprungs 94 ist eine Axialnut 96 ausgebildet, in der ein Dichtring 98 angeordnet ist, der bei der Befestigung des zweiten Gehäuseteils 62 am Außengehäuse 10 entsprechend verpresst wird, wobei das zweite Gehäuseteil 62 mit seiner Anschlussfläche 60 gegen eine Außenwand 100 des Außengehäuses 10 anliegt.For attachment of the two housing parts 40, 62 on the outer housing 10 and consequent to the arrangement of the control slide 28 in the outer housing 10, the outer housing 10 at its pump inlet 14 opposite axial end an opening 92 into which an annular projection 94 of the second housing part 62 such protrudes that the projection 94 abuts against the inner wall of the opening 92. Radial outside of this hollow cylindrical projection 94 an axial groove 96 is formed, in which a sealing ring 98 is arranged, which in the attachment of the second housing part 62 on the outer housing 10th is pressed accordingly, the second housing part 62 abuts with its connection surface 60 against an outer wall 100 of the outer housing 10.

Dieser Vorsprung 94 dient gleichzeitig als rückwärtiger Anschlag 102 für den Regelschieber 28, dessen äußere Umfangswand 44 sich mit ihrem zum Kühlmittelpumpenlaufrad 44 weisenden Ende mit etwas vergrößertem Durchmesser fortsetzt. Am inneren Umfang und am äußeren Umfang des Bodens 42 ist jeweils eine Radialnut 104, 106 ausgebildet, in der jeweils ein Kolbenring 108, 110 angeordnet ist, über die der Regelschieber 28 im radial inneren Bereich auf dem Vorsprung 38 des ersten Gehäuseteils 26 und im radial äußeren Bereich an einer Innenwand des in die Öffnung 92 des Außengehäuses 10 ragenden hohlzylindrischen Vorsprungs 94 des zweiten Gehäuseteils 62 gleitend gelagert und entsprechend dichtend geführt ist.This projection 94 also serves as a rear stop 102 for the control slide 28, the outer peripheral wall 44 continues with its pointing to the coolant pump impeller 44 end with a slightly larger diameter. At the inner circumference and at the outer circumference of the bottom 42, a radial groove 104, 106 is formed in each of which a piston ring 108, 110 is arranged, via which the control slide 28 in the radially inner region on the projection 38 of the first housing part 26 and in the radial outer region is slidably supported on an inner wall of the projecting into the opening 92 of the outer housing 10 hollow cylindrical projection 94 of the second housing part 62 and guided sealingly.

Aus der Öffnung 92 des Außengehäuses 10 ragt somit nach dem Einbau lediglich das hintere Stück der Antriebswelle 18 sowie der hintere Teil des zweiten Gehäuseteils 62, in dem das Magnetventil 66 aufgenommen ist und auf dem das Kugellager 26 aufgepresst ist, welches das Riemenrad 24 trägt. Die Antriebswelle 18 erstreckt sich unter Zwischenlage einer Dichtung 112 zentral durch die beiden Gehäuseteile 40, 62.Thus, after installation, only the rear part of the drive shaft 18 and the rear part of the second housing part 62 project from the opening 92 of the outer housing 10, in which the solenoid valve 66 is accommodated and on which the ball bearing 26 which carries the belt pulley 24 is pressed. The drive shaft 18 extends with the interposition of a seal 112 centrally through the two housing parts 40, 62nd

Die beschriebene Kühlmittelpumpe ist äußerst kompakt aufgebaut, jedoch einfach und kostengünstig herstellbar und montierbar, da eine geringe Teileanzahl vorliegt. Auf zusätzliche Leitungen zur hydraulischen Verbindung der Seitenkanalpumpe 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. Dadurch, dass der Regelschieber im inneren Bereich auf dem Gehäuseteil geführt wird, welches gleichzeitig den Seitenkanal ausbildet und radial begrenzt, kann der Regelschieber entlang dieser Begrenzungswand mit eindeutig definiertem Spiel und daraus folgend definierter Leckage geführt werden. Durch den axial sehr kurzen Aufbau aufgrund des einstückigen Laufrades für die Seitenkanalpumpe und die eigentliche Kühlmittelförderpumpe eignet sich diese besonderes zur Anordnung direkt in einer Öffnung des Kurbelgehäuses.The coolant pump described is extremely compact, but easy and inexpensive to manufacture and assemble, since a small number of parts is present. On additional lines for hydraulic connection of the side channel 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 fact that the control slide is guided in the inner region on the housing part, which simultaneously forms the side channel and radially limited, the control slide can along this Boundary wall with clearly defined game and consequent defined leakage out. Due to the axially very short design due to the one-piece impeller for the side channel pump and the actual coolant pump, this particular is suitable for the arrangement directly in an opening of the crankcase.

Es sollte deutlich sein, dass der Schutzbereich des Hauptanspruchs nicht auf das beschriebene Ausführungsbeispiel begrenzt ist, sondern verschiedene Modifikationen innerhalb des Schutzbereiches denkbar sind. So könnte auch lediglich ein Druckraum verwendet werden und eine Rückstellung des Regelschiebers über eine Feder erfolgen.It should be clear that the scope of the main claim is not limited to the described embodiment, but various modifications within the scope are conceivable. So only a pressure chamber could be used and carried out a provision of the control slide via a spring.

Claims (11)

  1. A coolant pump for an internal combustion engine, having a drive shaft (18),
    a coolant pump impeller (20) which is arranged at said drive shaft (18) at least in a rotationally fixed manner and by means of which a coolant is adapted to be delivered into a delivery duct (12) surrounding said coolant pump impeller (20),
    an adjustable control slide (28) by means of which a throughflow cross-section of an annular gap (30) between an outlet (32) of said coolant pump impeller (20) and said delivery duct (12) is adapted to be controlled,
    a side channel pump (56) having a side channel pump impeller (46) which is arranged at said drive shaft (18) at least in a rotationally fixed manner, a side channel (50) of said side channel pump (56) in which a pressure is adapted to be generated as a result of rotation of said side channel pump impeller (46),
    a pressure duct (72) via which an outlet (54) of said side channel (50) is adapted to be fluidically connected to a first pressure chamber (58) of said control slide (28),
    a valve (66) via which a throughflow cross-section (70) of said pressure duct (72) is adapted to be closed and opened,
    wherein
    said coolant pump impeller (20) is integrally formed with said side channel pump impeller (46) and said side channel (50) is formed in a first housing part (40) on which said control slide (28) is slidingly guided.
  2. The coolant pump for an internal combustion engine according to claim 1,
    characterized in that
    the blades (48) of the side channel pump impeller (46) are formed on a rear side of the coolant pump impeller (20) configured as a radial pump impeller and are arranged axially opposite to a side channel (50).
  3. The coolant pump for an internal combustion engine according to claim 2,
    characterized in that
    a radially outer boundary wall (78) of the side channel (50) extends axially towards the coolant pump impeller (20), radially surrounds the side channel pump impeller (46) and is radially surrounded by an outer circumferential wall (44) of the control slide (28).
  4. The coolant pump for an internal combustion engine according to any one of the preceding claims,
    characterized in that
    the control slide (28) is slidingly guided on an outer surface (36) of an axially extending annular projection (38) of the first housing part (40).
  5. The coolant pump for an internal combustion engine according to any one of the preceding claims,
    characterized in that
    the first pressure chamber (58) is formed on the axial side of the control slide (28) facing away from the coolant pump impeller (20) and the first housing part (40) delimits a second pressure chamber (64) towards a first axial side and the control slide (28) delimits it towards the opposite axial side.
  6. The coolant pump for an internal combustion engine according to any one of claims 4 and 5,
    characterized in that
    the annular projection (38) of the first housing part (40) delimits the two pressure chambers (58, 64) radially inwards.
  7. The coolant pump for an internal combustion engine according to any one of the preceding claims,
    characterized in that
    the pressure duct (72) extends through the annular projection (38) of the first housing part (40).
  8. The coolant pump for an internal combustion engine according to claim 7,
    characterized in that
    the pressure duct (72) extends from the outlet (54) of the side channel pump (56) through the first housing part (40) and a second housing part (62) into the first pressure chamber (58), wherein in said second housing part (62) the throughflow cross-section (70) governed by the valve (66) is formed.
  9. The coolant pump for an internal combustion engine according to any one of claims 4 and 8,
    characterized in that
    the annular projection (38) of the first housing part (40) comprises a shoulder (84) at its axial end, from which the annular projection (80), with a reduced diameter, further axially extends into a corresponding accommodation opening (82) of the second housing part (62) to which said first housing part (40) is fastened.
  10. The coolant pump for an internal combustion engine according to claim 9,
    characterized in that
    the first housing part (40) is fastened to the second housing part (62) by means of screws.
  11. The coolant pump for an internal combustion engine according to any one of the preceding claims,
    characterized in that
    in the first housing part (40) a connecting duct (74) is formed which extends from the side channel (50) through the first housing part (40) into the second pressure chamber (64).
EP16782281.6A 2015-11-06 2016-10-19 Coolant pump for an internal combustion engine Active EP3371461B1 (en)

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DE102015119097.4A DE102015119097B4 (en) 2015-11-06 2015-11-06 Coolant pump for an internal combustion engine
PCT/EP2016/075076 WO2017076645A1 (en) 2015-11-06 2016-10-19 Coolant pump for an internal combustion engine

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EP3371461B1 true EP3371461B1 (en) 2019-11-27

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EP (2) EP3371460B1 (en)
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US10982676B2 (en) 2021-04-20
US20180320692A1 (en) 2018-11-08
WO2017076524A1 (en) 2017-05-11
JP2018537609A (en) 2018-12-20
CN108291550A (en) 2018-07-17
WO2017076645A1 (en) 2017-05-11
JP2018530706A (en) 2018-10-18
CN108350886B (en) 2020-03-03
JP6574311B2 (en) 2019-09-11
JP6679718B2 (en) 2020-04-15
US10508650B2 (en) 2019-12-17
EP3371460A1 (en) 2018-09-12
EP3371461A1 (en) 2018-09-12
US20180320695A1 (en) 2018-11-08
CN108291550B (en) 2021-06-08
DE102015119097A1 (en) 2017-05-11
DE102015119097B4 (en) 2019-03-21
CN108350886A (en) 2018-07-31
EP3371460B1 (en) 2019-11-13

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