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EP3371460B1 - Coolant pump for the automotive industry - Google Patents

Coolant pump for the automotive industry Download PDF

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Publication number
EP3371460B1
EP3371460B1 EP16741314.5A EP16741314A EP3371460B1 EP 3371460 B1 EP3371460 B1 EP 3371460B1 EP 16741314 A EP16741314 A EP 16741314A EP 3371460 B1 EP3371460 B1 EP 3371460B1
Authority
EP
European Patent Office
Prior art keywords
coolant pump
channel
housing part
side channel
automotive industry
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.)
Active
Application number
EP16741314.5A
Other languages
German (de)
French (fr)
Other versions
EP3371460A1 (en
Inventor
Stephan Zielberg
Michael-Thomas Benra
Stefan Rothgang
Andreas Burger
Helmut Prinz
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Pierburg GmbH
Original Assignee
Pierburg GmbH
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Filing date
Publication date
Application filed by Pierburg GmbH filed Critical Pierburg GmbH
Publication of EP3371460A1 publication Critical patent/EP3371460A1/en
Application granted granted Critical
Publication of EP3371460B1 publication Critical patent/EP3371460B1/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 the motor vehicle sector with a drive shaft, a coolant pump impeller which is at least rotatably mounted on the drive shaft and via which coolant in a conveying channel surrounding the coolant pump impeller is conveyed, an adjustable control slide, via which a flow cross-section of an annular gap between a Outlet of the coolant pump impeller 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%kanalpumpenlaufrades a pressure can be generated, wherein the side channel has an inlet and an outlet, a pressure channel, via which the outlet of the side channel is fluidically connectable to a first pressure chamber of the control slide, and a valve, via which a flow cross section of the pressure channel versc can be left and released.
  • Such coolant pumps serve, for example, in internal combustion engines to regulate the quantity of the delivered 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 amount of coolant conveyed to the coolant requirement of the internal combustion engine or the motor vehicle adapt.
  • 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.
  • 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 connecting channel is designed as a bore.
  • the connecting channel is arranged approximately centrally between the inlet and the outlet.
  • the connecting channel thus acts as a fail-safe device, which ensures that when the solenoid valve in each Operating situation of the full volume flow of the coolant pump is provided.
  • the exact positioning of the connection channel is dependent on the pressure gradient in the side channel.
  • 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 in accordance with the gap between the slider and the rotating side channel pump impeller and thus
  • this wall can be used as a guide for the control slide between the pressure generating coolant flow and the flow rate of the main pump.
  • the first pressure chamber is formed on the axial side of the control slide facing away from the coolant pump impeller.
  • the adjustment of the control slide can be done completely in accordance with hydraulic forces, which 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.
  • control slide is slidably guided on an outer surface of an annular, axially extending projection of the first housing part.
  • 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 outer surface may also have a coating.
  • 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.
  • 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 extends the annular projection of reduced diameter further axially into a corresponding receiving opening of the second housing part to which the first housing part is fixed.
  • 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.
  • the coolant pump according to the invention is simple and inexpensive to manufacture and assemble.
  • a coolant pump 2 consists of an outer housing 10, in which a spiral conveying channel 12 is formed, into which a coolant is sucked via an axial pump inlet 14 likewise formed in the outer housing 10, which coolant flows via the conveying channel 12 to a tangential pump outlet 16 formed in the outer housing 10 and is conveyed into a cooling circuit of an internal combustion engine.
  • This outer housing 10 can in particular be formed by a cylinder crankcase, which has a recess for receiving the remaining coolant pump.
  • a coolant pump impeller 20 is mounted radially on the inside of the conveying channel 12 on a drive shaft 18, which is designed as a radial impeller, by the rotation of the promotion of the coolant 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 mechanically 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.
  • this control slide 28 In order to operate this control slide 28 is at the pump inlet 14 opposite axial side of the Coolant pump impeller 20 integrally formed with the coolant pump impeller 20, a side channel pump impeller 46 which is driven in accordance with the coolant pump impeller 20.
  • This 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 Rare Kanalpumpenankhamrad 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 conveyed through the side channel pump 56 coolant which generates a hydraulic pressure can now either a first pressure chamber 58 are supplied, which on the side facing away from the coolant pump impeller 20 side of the control slide 28 between the bottom 42 of the control slide 28 and a pad 60 of a second housing part 62nd is formed or returned via a solenoid valve 66 of the coolant pump 2.
  • a second pressure chamber 64 which is arranged between the bottom 42 of the control slide 28 and the first housing part 40, there is a speed-dependent hydraulic pressure.
  • a receptacle 65 for the valve 66 is provided with respect to the pressure chamber 58 in the second housing part 62, which serves as a 3/2-way solenoid valve is formed and has a connection to the pressure chamber 58, so that depending on the position of its closing body 68, a flow cross-section 70 of a pressure channel 72 is controlled.
  • a Connecting passage 74 is provided, which serves as a fail-safe hole, as this pressure in the space 64, a pressure is provided which is always greater than the suction pressure of the side channel pump 56.
  • the 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 connecting channel 74 extends from a portion of the inlet 52 from the side channel 50 directly into the second pressure chamber 64.
  • This connecting channel 74 is located approximately in the middle, approximately at 150 ° to the inlet 52, between this and the outlet 54.
  • the connecting channel 74 thus acts as a fail-safe device, which ensures that when switched off or disturbed solenoid valve 66 in any operating situation in the pressure chamber 64, a speed-dependent pressure prevails, which is greater than the intake pressure of the side channel pump 56 and thus also the coolant pump 2 in any case, since this pressure yes prevails in the first pressure chamber 58.
  • the exact positioning of the connecting channel is dependent on the pressure gradient in the side channel 50.
  • a third, not shown, flow connection of the solenoid valve 66 leads to the suction side of the coolant pump. 2
  • the annular gap 30 at the outlet 32 of the coolant pump impeller 20 is fully released by the solenoid valve 66 is not energized, whereby the closing body 68 moved due to a spring force in its the flow cross-section 70 of the pressure channel 72 occlusive position becomes.
  • 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 moved to its annular gap 30 releasing position and thus a maximum delivery of the coolant pump 2 is ensured.
  • the control slide 28 In case of failure of the electrical supply of the solenoid valve 66, the control slide 28 correspondingly assumes the same position, so that even in this emergency operation, a maximum delivery of the coolant pump 2 is ensured without the need for a return spring or other, non-hydraulic force would be necessary.
  • 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 40 and via a bore in the coolant pump impeller 20 to the pump inlet 14 of the coolant pump 2 leads.
  • 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 in order to displace the control slide 28 into the annular gap 30. 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.
  • valve 66 If a controllable solenoid valve 66 is used, it is also possible to move the valve 66 in intermediate positions, whereby an equilibrium of forces can be achieved for each position of the control slide 28, so that complete regulation 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 with an annular projection 80, the reduced diameter from the annular projection 38 further in from Coolant pump impeller remote end extends, is pushed into a radially inner receiving opening 82 of the second housing part 62 until the first housing part 40 abuts with its formed between the projections 38, 80 paragraph 84 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 is pressed correspondingly in the attachment of the second housing part 62 on the outer housing 10, wherein the second housing part 62 with its connection surface 60 against an outer wall 100 of the outer housing 10 is present.
  • 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 20 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 on an inner wall of projecting into the opening 92 of the outer housing 10 hollow cylindrical projection 94 of the second housing part 62 is slidably mounted and guided in accordance with sealing.
  • the coolant pump 2 described is extremely compact, but easy and inexpensive to produce 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 den KFZ-Bereich 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, wobei der Seitenkanal einen Einlass und einen Auslass aufweist, einem Druckkanal, über welchen der 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 the motor vehicle sector with a drive shaft, a coolant pump impeller which is at least rotatably mounted on the drive shaft and via which coolant in a conveying channel surrounding the coolant pump impeller is conveyed, an adjustable control slide, via which a flow cross-section of an annular gap between a Outlet of the coolant pump impeller 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, wherein the side channel has an inlet and an outlet, a pressure channel, via which the outlet of the side channel is fluidically connectable to a first pressure chamber of the control slide, and a valve, via which a flow cross section of the pressure channel versc can be left and released.

Derartige Kühlmittelpumpen dienen beispielweise 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 serve, for example, in internal combustion engines to regulate the quantity of the delivered 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 amount of coolant conveyed to the coolant requirement of the internal combustion engine or the motor vehicle adapt. To avoid increased pollutant emissions and reduction of fuel consumption, in particular the cold running phase of the engine should be shortened. This is done, inter alia, by 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 to provide the amount of coolant required for moving the slide does not need to be provided via additional conveyor units, such as additional piston / cylinder units or other hydraulic fluids for Having to compress actuation, 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 entsprechenden Anordnung eines Zylinderkurbelgehäuse angeordnet und montiert werden könnte. Ein weiterer Nachteil bei einer derartigen Pumpe, die durch den Verbrennungsmotor antreibbar ist, ist die Tatsache, dass in bestimmten Drehzahlbereichen der Druck in der Seitenkanalpumpe wesentlich geringer als der Druck im ersten Druckraum ist, was dazu führt, dass trotz eines Kühlbedarfes der Regelschieber den Förderkanal verschließt. Zur Lösung dieses Problems sieht die DE 10 2012 207 387 A1 vor, dass ein mit der Druckseite der Seitenkanalpumpe verbundenes Rückschlagventil vorgesehen ist, dass bei zu hohem Druck in der Seitenkanalpumpe öffnet. Es sollte deutlich sein, dass ein derartiges Rückschlagventil den Aufbau der Kühlmittelpumpe zusätzlich verkompliziert. Darüber hinaus wird durch ein derartiges Rückschlagventil zusätzlicher Bauraum benötigt.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. Another disadvantage with such a pump, which is drivable by the internal combustion engine, is the fact that in certain Speed ranges of the pressure in the side channel pump is substantially lower than the pressure in the first pressure chamber, which means that despite a cooling requirement of the control slide closes the conveyor channel. To solve this problem sees the DE 10 2012 207 387 A1 that a non-return valve connected to the pressure side of the side channel pump is provided that opens at too high pressure in the side channel pump. It should be clear that such a check valve further complicates the structure of the coolant pump. In addition, additional space is required by such a check valve.

Es stellt sich daher die Aufgabe, eine Kühlmittelpumpe für den KFZ-Bereich zu schaffen, bei der der Montageaufwand und der benötigte Bauraum deutlich reduziert werden. Insbesondere soll gewährleistet sein, dass der Kühlmittelfluss in jeder Betriebssituation des Verbrennungsmotors, wenn gewollt, gesichert ist.It is therefore the object to provide a coolant pump for the motor vehicle sector, in which the installation effort and the required space can be significantly reduced. In particular, it should be ensured that the coolant flow in each operating situation of the internal combustion engine, if desired, is secured.

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 zwischen dem Einlass und dem Auslass ein Verbindungskanal vom Seitenkanal in einen zweiten Druckraum vorgesehen ist, wobei der zweite Druckraum an einer der Kühlmittelpumpenlaufrad zugewandten Seite des Regelschiebers vorgesehen ist, ist eine besonders einfache konstruktive Lösung für ein ungünstiges Druckverhältnis entwickelt worden, die keinen zusätzlichen Bauraum benötigt und darüber hinaus störunanfällig ist.Characterized in that between the inlet and the outlet, a connecting channel from the side channel is provided in a second pressure chamber, wherein the second pressure chamber is provided on a coolant pump impeller side facing the control slide, a particularly simple constructive solution has been developed for an unfavorable pressure ratio, the no requires additional space and is beyond störunanfällig.

Hinsichtlich einer einfachen Fertigung ist der Verbindungskanal als Bohrung ausgeführt. In einer besonders vorteilhaften Ausführungsform ist der Verbindungskanal in etwa mittig zwischen Einlass und dem Auslass angeordnet. Der Verbindungskanal wirkt somit als Fail-Safe- Einrichtung, die gewährleistet, dass bei ausgeschaltetem Magnetventil in jeder Betriebssituation der volle Volumenstrom der Kühlmittelpumpe bereitgestellt wird. Die genaue Positionierung des Verbindungskanals Ist hierbei abhängig von dem Druckgradienten im Seitenkanal.With regard to a simple production of the connecting channel is designed as a bore. In a particularly advantageous embodiment, the connecting channel is arranged approximately centrally between the inlet and the outlet. The connecting channel thus acts as a fail-safe device, which ensures that when the solenoid valve in each Operating situation of the full volume flow of the coolant pump is provided. The exact positioning of the connection channel is dependent on the pressure gradient in the side channel.

In einer besonders vorteilhaften Ausführungsform einer erfindungsgemäßen Kühlmittelpumpe ist das Kühlmittelpumpenlaufrad einstückig mit dem Seitenkanalpumpenlaufrad ausgebildet und ist der Seitenkanal in einem ersten Gehäuseteil ausgebildet, auf dem der Regelschieber gleitend geführt ist. Hierdurch 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.In a particularly advantageous embodiment of a coolant pump according to the invention, 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. As a result, 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. Hierbei ist vorteilhafterweise der zweite Druckraum zwischen einem Boden des Regelschiebers und einem ersten Gehäuseteil, in dem der Seitenkanal vorgesehen ist, angeordnet.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. Here, advantageously, the second pressure space between a bottom of the control slide and a first housing part, in which the side channel is provided, arranged.

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 in accordance with the gap between the slider and the rotating side channel pump impeller and thus In addition, this wall can be used as a guide for the control slide between the pressure generating coolant flow and the flow rate of the main pump.

Vorzugsweise ist der erste Druckraum an der vom Kühlmittelpumpenlaufrad abgewandten axialen Seite des Regelschiebers ausgebildet. 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 of the control slide facing away from the coolant pump impeller. The adjustment of the control slide can be done completely in accordance with hydraulic forces, which 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.

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 Außenfläche kann jedoch auch eine Beschichtung aufweisen. Auch der Einsatz eines Gleitwerkstoffes aus Metall oder Kunststoff ist denkbar. 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 is particularly advantageous if the control slide is slidably guided on an outer surface of an annular, axially extending projection of the first housing part. 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. However, this outer surface may also have a coating. The use of a sliding material made of metal or plastic is conceivable. 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.

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 der ringförmige 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 extends the annular projection of reduced diameter further axially into a corresponding receiving opening of the second housing part to which the first housing part is fixed. There is accordingly via 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.

Es wird somit eine Kühlmittelpumpe für den KFZ-Bereich 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 the motor vehicle area, 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. Hierbei zeigt:

  • Figur 1 eine Seitenansicht einer erfindungsgemäßen Kühlmittelpumpe in geschnittener Darstellung,
  • Figur 2 eine zu Figur 1 gedrehte Seitenansicht der erfindungsgemäßen Kühlmittelpumpe in geschnittener Darstellung,
  • Figur 3 eine im Bereich einer Seitenkanalpumpe der Kühlmittelpumpe geschnittene Vorderansicht, und
  • Figur 4 eine zu Figur 1 gedrehte Teilansicht 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. Hereby shows:
  • FIG. 1 a side view of a coolant pump according to the invention in a sectional view,
  • FIG. 2 one too FIG. 1 rotated side view of the coolant pump according to the invention in a sectional view,
  • FIG. 3 a cut in the region of a side channel pump of the coolant pump front view, and
  • FIG. 4 one too FIG. 1 rotated partial view of the coolant pump according to the invention in a sectional view.

Eine erfindungsgemäße Kühlmittelpumpe 2 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 einer Verbrennungskraftmaschine gefördert wird. Dieses Außengehäuse 10 kann insbesondere durch ein Zylinderkurbelgehäuse gebildet sein, welches eine Ausnehmung zur Aufnahme der übrigen Kühlmittelpumpe aufweist.A coolant pump 2 according to the invention consists of an outer housing 10, in which a spiral conveying channel 12 is formed, into which a coolant is sucked via an axial pump inlet 14 likewise formed in the outer housing 10, which coolant flows via the conveying channel 12 to a tangential pump outlet 16 formed in the outer housing 10 and is conveyed into a cooling circuit of an internal combustion engine. This outer housing 10 can 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, weiches als Radialpumpenrad ausgebildet ist, durch dessen Drehung die Förderung des Kühlmittels im Förderkanal 12 erfolgt.For this purpose, a coolant pump impeller 20 is mounted radially on the inside of the conveying channel 12 on a drive shaft 18, which is designed as a radial impeller, by the rotation of the promotion of the coolant 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 2 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 volumetric flow conveyed by the coolant pump 2, 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 mechanically 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 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 Seltenkanalpumpenlaufrad 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 is at the pump inlet 14 opposite axial side of the Coolant pump impeller 20 integrally formed with the coolant pump impeller 20, a side channel pump impeller 46 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 Rare Kanalpumpenlaufrad 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.

Das durch die Seitenkanalpumpe 56 geförderte Kühlmittel, das einen hydraulischen Druck erzeugt, 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 über ein Magnetventil 66 der Kühlmittelpumpe 2 zurückgeführt werden. In einem zweiten Druckraum 64, der zwischen dem Boden 42 des Regelschiebers 28 und dem ersten Gehäuseteil 40 angeordnet ist, herrscht ein drehzahlabhängiger hydraulischer Druck. Um durch das geförderte Kühlmittel der Seitenkanalpumpe 56 die Drücke in den Druckräumen 58, 64 gezielt zu steuern oder zu regeln, ist hinsichtlich des Druckraumes 58 im zweiten Gehäuseteil 62 eine Aufnahme 65 für das Ventil 66 vorgesehen, welches als 3/2-Wege-Magnetventil ausgebildet ist und eine Verbindung zu dem Druckraum 58 aufweist, so dass je nach Position seines Schließkörpers 68 ein Durchströmungsquerschnitt 70 eines Druckkanals 72 geregelt wird. Zur Druckregelung oder -steuerung des Druckes im Druckraum 64 ist ein Verbindungskanal 74 vorgesehen, der als Fail-Safe-Bohrung dient, da hierdurch im Druckraum 64 ein Druck bereitgestellt ist, der immer größer als der Ansaugdruck der Seitenkanalpumpe 56 ist.The conveyed through the side channel pump 56 coolant which generates a hydraulic pressure can now either a first pressure chamber 58 are supplied, which on the side facing away from the coolant pump impeller 20 side of the control slide 28 between the bottom 42 of the control slide 28 and a pad 60 of a second housing part 62nd is formed or returned via a solenoid valve 66 of the coolant pump 2. In a second pressure chamber 64, which is arranged between the bottom 42 of the control slide 28 and the first housing part 40, there is a speed-dependent hydraulic pressure. In order to selectively control or regulate the pressures in the pressure chambers 58, 64 by the pumped coolant of the side channel pump 56, a receptacle 65 for the valve 66 is provided with respect to the pressure chamber 58 in the second housing part 62, which serves as a 3/2-way solenoid valve is formed and has a connection to the pressure chamber 58, so that depending on the position of its closing body 68, a flow cross-section 70 of a pressure channel 72 is controlled. For pressure control or control of the pressure in the pressure chamber 64 is a Connecting passage 74 is provided, which serves as a fail-safe hole, as this pressure in the space 64, a pressure is provided which is always greater than the suction pressure of the side channel pump 56.

Der 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.The 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.

Wie insbesondere aus den Figuren 3 und 4 hervorgeht, ist der zweite Druckraum 64 über den Verbindungskanal 74, welcher im ersten Gehäuseteil 40 ausgebildet ist, mit dem Seitenkanal 50 verbunden, wobei dieser Verbindungskanal 74 sich von einem Bereich des Einlasses 52 aus dem Seitenkanal 50 direkt in den zweiten Druckraum 64 erstreckt. Dieser Verbindungskanal 74 befindet sich in etwa mittig, in etwa 150° versetzt zum Einlass 52, zwischen diesem und dem Auslass 54. Der Verbindungskanal 74 wirkt somit als Fail-Safe-Einrichtung, die gewährleistet, dass bei ausgeschaltetem oder gestörtem Magnetventil 66 in jeder Betriebssituation im Druckraum 64 ein drehzahlabhängiger Druck vorherrscht, der in jedem Fall größer als der Ansaugdruck der Seitenkanalpumpe 56 und damit auch der Kühlmittelpumpe 2 ist, da dieser Druck ja im ersten Druckraum 58 vorherrscht. Die genaue Positionierung des Verbindungskanals ist hierbei abhängig von dem Druckgradienten im Seitenkanal 50. Ein dritter, nicht dargestellter Strömungsanschluss des Magnetventils 66 führt zur Saugseite der Kühlmittelpumpe 2.As in particular from the FIGS. 3 and 4 shows, the second pressure chamber 64 via the connecting channel 74, which is formed in the first housing part 40, connected to the side channel 50, said connecting channel 74 extends from a portion of the inlet 52 from the side channel 50 directly into the second pressure chamber 64. This connecting channel 74 is located approximately in the middle, approximately at 150 ° to the inlet 52, between this and the outlet 54. The connecting channel 74 thus acts as a fail-safe device, which ensures that when switched off or disturbed solenoid valve 66 in any operating situation in the pressure chamber 64, a speed-dependent pressure prevails, which is greater than the intake pressure of the side channel pump 56 and thus also the coolant pump 2 in any case, since this pressure yes prevails in the first pressure chamber 58. The exact positioning of the connecting channel is dependent on the pressure gradient in the side channel 50. A third, not shown, flow connection of the solenoid valve 66 leads to the suction side of the coolant pump. 2

Soll die Kühlmittelpumpe 2 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 2 abströmen kann. Stattdessen fördert In diesem Zustand die Seitenkanalpumpe 56 gegen den geschlossenen Durchströmungsquerschnitt 70 des Druckkanals 72 mit einem drehzahlabhängigen Druckverlauf, wobei abhängig von der genauen Positionierung des Verbindungskanals 74 im zweiten Druckraum 64 ein entsprechender Druck vorherrscht. 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 2 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 2 sichergestellt wird, ohne dass hierzu eine Rückstellfeder oder eine andere, nicht hydraulische Kraft notwendig wäre.If the coolant pump 2 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 not energized, whereby the closing body 68 moved due to a spring force in its the flow cross-section 70 of the pressure channel 72 occlusive position becomes. As a result, no pressure is built up by the coolant in the first pressure chamber 58, but the coolant present in the pressure chamber 58 can flow out to the pump inlet 14 of the coolant pump 2 via the not shown other flow connection of the solenoid valve 66, which is released in this state , Instead promotes In this state, the side channel pump 56 against the closed flow cross-section 70 of the pressure channel 72 with a speed-dependent pressure profile, which prevails depending on the exact positioning of the connecting channel 74 in the second pressure chamber 64, a corresponding pressure. 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 moved to its annular gap 30 releasing position and thus a maximum delivery of the coolant pump 2 is ensured. In case of failure of the electrical supply of the solenoid valve 66, the control slide 28 correspondingly assumes the same position, so that even in this emergency operation, a maximum delivery of the coolant pump 2 is ensured without the need for a return spring or other, non-hydraulic force would be necessary.

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 2 führt.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 40 and via a bore in the coolant pump impeller 20 to the pump inlet 14 of the coolant pump 2 leads.

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, um den Regelschieber 28 in den Ringspalt 30 zu verschieben. 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.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 in order to displace the control slide 28 into the annular gap 30. 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.

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 move the valve 66 in intermediate positions, whereby an equilibrium of forces can be achieved for each position of the control slide 28, so that complete regulation 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 with an annular projection 80, the reduced diameter from the annular projection 38 further in from Coolant pump impeller remote end extends, is pushed into a radially inner receiving opening 82 of the second housing part 62 until the first housing part 40 abuts with its formed between the projections 38, 80 paragraph 84 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 is pressed correspondingly in the attachment of the second housing part 62 on the outer housing 10, wherein the second housing part 62 with its connection surface 60 against an outer wall 100 of the outer housing 10 is present.

Dieser Vorsprung 94 dient gleichzeitig als rückwärtiger Anschlag 102 für den Regelschieber 28, dessen äußere Umfangswand 44 sich mit ihrem zum Kühlmittelpumpenlaufrad 20 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 20 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 on an inner wall of projecting into the opening 92 of the outer housing 10 hollow cylindrical projection 94 of the second housing part 62 is slidably mounted and guided in accordance with sealing.

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 2 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 2 described is extremely compact, but easy and inexpensive to produce 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. Characterized in 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 be performed along this boundary wall with clearly defined game and consequent defined leakage. 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.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.

Claims (14)

  1. Coolant pump for the automotive industry, comprising a drive shaft (18), a coolant pump impeller (20), which is arranged on the drive shaft (18) at least for conjoint rotation and by means of which coolant can be conveyed into a conveying channel (12) surrounding the coolant pump impeller (20), a movable control slide (28), by means of which a flow cross-section of an annular gap (30) between an exit (32) of the coolant pump impeller (20) and the conveying channel (12) can be controlled, a side channel pump (56) having a side channel pump impeller (46), which is arranged on the drive shaft (18) at least for conjoint rotation, a side channel (50) of the side channel pump (56), in which a pressure can be generated by rotation of the side channel pump impeller (46), wherein the side channel has an inlet (52) and an outlet (54), a pressure channel (72), by means of which the outlet (54) of the side channel (50) can be fluidically connected to a first pressure chamber (58) of the control slide (28), a valve (66), by means of which a flow cross-section (70) of the pressure channel (72) can be closed and opened, characterized in that a connection channel (74) from the side channel (50) into a second pressure chamber (64) is provided between the inlet (52) and the outlet (54), wherein the second pressure chamber (64) is provided on a side of the control slide (28) facing the coolant pump impeller (20).
  2. Coolant pump for the automotive industry according to claim 1, characterized in that the connecting channel (74) is designed as a bore.
  3. Coolant pump for the automotive industry according to claim 1 or 2, characterized in that the connecting channel is arranged approximately centrally between the inlet (52) and the outlet (54).
  4. Coolant pump for the automotive industry according to one of claims 1 to 2, characterized in that the coolant pump impeller (20) is formed integrally with the side channel pump impeller (46) and the side channel (50) is formed in a first housing part (40) an which the control slide (28) is slidably guided.
  5. Coolant pump for the automotive industry according to claim 4, 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) formed as a radial pump impeller, and that the blades are arranged axially opposite a side channel (50).
  6. Coolant pump for the automotive industry according to one of claims 4 or 5, characterized in that the second pressure chamber is arranged between a bottom (42) of the control slide (28) and a first housing part (40) in which the side channel (50) is provided.
  7. Coolant pump for the automotive industry according to one of claims 4 to 6, characterized in that a radially outer delimiting wall (78) of the side channel (50) extends axially in the direction of the coolant pump impeller (20), surrounds the side channel pump impeller (46) radially and is radially surrounded by an outer circumferential wall (44) of the control slide (28).
  8. Coolant pump for the automotive industry according to one of claims 4 to 7, characterized in that the first pressure chamber (58) is formed on the axial side of the control slide (28) averted from the coolant pump impeller (20).
  9. Coolant pump for the automotive industry according to one of claims 4 to 8, characterized in that the control slide (28) is slidably guided on an outer surface (36) of an annular, axially extending projection (38) of the first housing part (40).
  10. Coolant pump for the automotive industry according to claim 9, characterized in that the annular projection (38) of the first housing part (40) delimits the two pressure chambers (58, 64) radially inward.
  11. Coolant pump for the automotive industry according to claim 9 or 10, characterized in that the pressure channel (72) extends through the annular projection (38) of the first housing part (40).
  12. Coolant pump for the automotive industry according to claim 11, characterized in that the pressure channel (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 the flow cross section (70) controlled by the valve (66) is formed in the second housing part (62).
  13. Coolant pump for the automotive industry according to one of claims 9 to 12, characterized in that the annular projection (38) of the first housing part (40) has a shoulder (84) at its axial end, from which the annular projection (80) extends further axially into a corresponding receiving opening (82) of the second housing part (62) to which the first housing part (40) is fastened.
  14. Coolant pump for the automotive industry according to claim 13, characterized in that the first housing part (40) is fastened to the second housing part (62) by means of screws (86).
EP16741314.5A 2015-11-06 2016-07-21 Coolant pump for the automotive industry Active EP3371460B1 (en)

Applications Claiming Priority (2)

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DE102015119097.4A DE102015119097B4 (en) 2015-11-06 2015-11-06 Coolant pump for an internal combustion engine
PCT/EP2016/067372 WO2017076524A1 (en) 2015-11-06 2016-07-21 Coolant pump for the automotive industry

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EP3371460A1 EP3371460A1 (en) 2018-09-12
EP3371460B1 true EP3371460B1 (en) 2019-11-13

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EP16782281.6A Active EP3371461B1 (en) 2015-11-06 2016-10-19 Coolant pump for an internal combustion engine

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EP (2) EP3371460B1 (en)
JP (2) JP6574311B2 (en)
CN (2) CN108350886B (en)
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DE102015119097B4 (en) * 2015-11-06 2019-03-21 Pierburg Gmbh Coolant pump for an internal combustion engine
DE102015119098B4 (en) * 2015-11-06 2019-03-21 Pierburg Gmbh Control arrangement for a mechanically controllable coolant pump of an internal combustion engine
DE102016222288A1 (en) * 2016-11-14 2018-05-17 Mahle International Gmbh pump means
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WO2017076645A1 (en) 2017-05-11
DE102015119097A1 (en) 2017-05-11
JP6574311B2 (en) 2019-09-11
WO2017076524A1 (en) 2017-05-11
CN108350886B (en) 2020-03-03
JP2018530706A (en) 2018-10-18
US10982676B2 (en) 2021-04-20
EP3371460A1 (en) 2018-09-12
CN108350886A (en) 2018-07-31
DE102015119097B4 (en) 2019-03-21
JP6679718B2 (en) 2020-04-15
JP2018537609A (en) 2018-12-20
US10508650B2 (en) 2019-12-17
US20180320695A1 (en) 2018-11-08
CN108291550A (en) 2018-07-17
EP3371461A1 (en) 2018-09-12
CN108291550B (en) 2021-06-08
US20180320692A1 (en) 2018-11-08
EP3371461B1 (en) 2019-11-27

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