EP3290713B1 - Coolant pump assembly for the automotive sector and a coolant circuit for a combustion engine - Google Patents

Coolant pump assembly for the automotive sector and a coolant circuit for a combustion engine Download PDF

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Publication number
EP3290713B1
EP3290713B1 EP17186282.4A EP17186282A EP3290713B1 EP 3290713 B1 EP3290713 B1 EP 3290713B1 EP 17186282 A EP17186282 A EP 17186282A EP 3290713 B1 EP3290713 B1 EP 3290713B1
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EP
European Patent Office
Prior art keywords
coolant
side channel
housing part
coolant pump
channel
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
EP17186282.4A
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German (de)
French (fr)
Other versions
EP3290713A1 (en
Inventor
Stefan Rothgang
Stephan Zielberg
Andreas Burger
DR. Michael BECKER
Michael-Thomas Benra
Simon Eglseer
Jürgen LANGTHALER
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
Bayerische Motoren Werke AG
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Pierburg GmbH
Bayerische Motoren Werke AG
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Publication of EP3290713A1 publication Critical patent/EP3290713A1/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
    • 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
    • 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
    • F05D2270/30—Control parameters, e.g. input parameters
    • F05D2270/303—Temperature
    • F05D2270/3032—Temperature excessive temperatures, e.g. caused by overheating
    • 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 arrangement for the automotive sector, which has a housing assembly with a main pump and a secondary pump designed as a side channel pump, with a main inlet and a main outlet, which are fluidically connectable to a main coolant circuit, with a drive shaft, with a Coolant pump impeller of the main pump, which is arranged at least in a rotationally fixed manner on the drive shaft and via which coolant can be conveyed into a delivery channel surrounding the coolant pump impeller, with an adjustable control slide, via which a flow cross section of an annular gap between an outlet of the coolant pump impeller and the delivery channel can be regulated, with a side channel pump with a side channel pump impeller, which is at least rotatably arranged on the drive shaft, with a side channel of the side channel pump, in which a Dru by rotating the side channel pump impeller ck can be generated, the side channel having a side inlet and at least one side outlet, with a pressure channel, via which a side outlet of the side
  • Such coolant pump arrangements are used, for example, in internal combustion engines to regulate the quantity of coolant delivered in a coolant circuit in order to prevent the internal combustion engine from overheating.
  • These pumps are usually driven by a Belt or chain drive so that the coolant pump wheel is driven at the speed of the crankshaft or at a fixed ratio to the speed of the crankshaft.
  • the amount of coolant delivered must be adapted to the coolant requirements of the internal combustion engine or the motor vehicle.
  • the engine's cold running phase should be shortened in particular. This is done, among other things, by throttling the coolant flow or completely switching it off during this phase.
  • pump arrangements for supplying the coolant circuit have become known for regulating the amount of coolant.
  • pump arrangements which can be coupled to or separated from their drive via couplings, in particular hydrodynamic couplings.
  • a particularly cost-effective and simply constructed option for regulating the conveyed coolant flow is the use of an axially displaceable control slide, which is connected to the coolant pump impeller is pushed so that to reduce the coolant flow, the pump does not deliver into the surrounding delivery channel, but against the closed slide.
  • sliders are also regulated in different ways.
  • a hydraulic adjustment of the slide has proven itself. This usually takes place via an annular piston chamber, which is filled with a hydraulic fluid and whose piston is connected to the slide, so that when the space is filled, the slide is moved over the impeller.
  • the slide is reset 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 reset the slide.
  • mechanically controllable coolant pumps are known, on the drive shaft of which 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.
  • FIG DE 10 2012 207 387 A1 Such a coolant device with a side channel pump acting as a secondary pump is shown in FIG DE 10 2012 207 387 A1 known.
  • this pump there is a slide on the back of the pump, which can be moved via a pressure in an annular chamber and can be reset via a spring.
  • This annular chamber is formed in a housing, which in turn is arranged on the rear of the slide and in which a first side channel of the side channel pump is also arranged, which is correspondingly opposite to the side channel pump impeller arranged on the shaft.
  • a second side channel is formed in a further housing part on the side opposite the side channel pump impeller.
  • a 3/2-way valve in this pump closes a pressure side of the side channel pump in a first position and connects a suction side of the pump to the cooling circuit and the slide, and in a second position the pressure side to the ring chamber of the slide and the suction side to the cooling circuit connected.
  • the side channel has a second secondary outlet, which can be connected to the main coolant circuit via an auxiliary coolant line, creates a very compact pump arrangement which, on the one hand, enables particularly simple and efficient control of the main coolant flow and, on the other hand, constant circulation of the coolant, at least in some areas of the cooling circuit guaranteed even when the main coolant flow is closed. In addition, the space required is kept small.
  • a particularly compact coolant pump arrangement is provided in that the coolant pump impeller is formed in one piece with the side channel pump impeller and the side channel is formed in a first housing part on which the control slide slides is led.
  • the first housing part takes on both the function as a flow housing and as a bearing for the slide, so that short pressure channels can be realized.
  • the blades of the side channel pump impeller are preferably formed on a rear side of the coolant pump impeller designed as a radial pump impeller and are arranged axially opposite the side channel.
  • the purely axial alignment of the side channel for blading reduces the radial space required, since no radially outer overflow channel is required. Accordingly, a maximum pressure can be generated for the existing installation space.
  • a connecting channel from the side channel into a second pressure chamber is provided between the secondary inlet and the secondary outlet, the second pressure chamber being formed between a bottom of the control slide and the first housing part in which the side channel is arranged.
  • the connecting channel is advantageously designed as a bore.
  • the side channel prefferably has a second secondary inlet.
  • a radially outer boundary wall of the side channel extends axially in the direction of the coolant pump impeller, radially surrounds the side channel pump impeller and is radially surrounded by a radially outer peripheral wall of the control slide.
  • This wall accordingly fills the gap between the slide and the rotating side channel pump impeller and thus between the pressure-generating coolant flow and the delivery flow of the main pump.
  • This wall can also be used as a guide for the control slide.
  • control slide 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 accordingly enables the control slide to be mounted internally on the advantageously machined outer surface.
  • This inner mounting of the control slide simplifies installation in a receiving opening of a cylinder crankcase, the inner surfaces of which then do not have to be machined. Furthermore, such an internal guide results in a very exact axial movement without fear of tilting or tilting of the control slide, since a sufficiently long guide surface is always available despite the small installation space used.
  • the first pressure chamber is preferably formed on the axial side of the control slide facing away from the coolant pump impeller, and the first housing part delimits a second pressure chamber to a first axial side and the control slide to the opposite axial side. Accordingly, the control slide can be adjusted entirely via hydraulic forces, which are only supplied to the corresponding pressure chambers. Additional annular spaces or piston spaces do not have to be formed. Due to the limitation by the first housing part, the fluidic connection to the pressure chambers can be established via a simple bore in this housing part, so that additional lines are not required.
  • the annular projection of the first housing part preferably delimits the two pressure spaces radially inward. Additional Seals in this area are accordingly not required. 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 have to be installed here either, but the first pressure chamber can also be fluidly connected directly to the side channel of the pump via the holes in the housing.
  • the pressure channel advantageously extends from the secondary outlet of the side channel pump through the first housing part and a second housing part into the first pressure chamber, the flow cross section controlled by the valve being formed in the second housing part.
  • the control valve can also be arranged accordingly in the housing, so that additional connections to the valve are also omitted here.
  • the annular projection of the first housing part preferably has a shoulder at its axial end, from which the annular projection with a reduced diameter extends further axially into a corresponding receiving opening of the second housing part, to which the first housing part is fastened. Accordingly, there is a direct centering of the two housing parts relative to one another via the inner projection, as a result of which the reception and guidance of the control slide is improved. This can be manufactured with small tolerances, so that a high level of tightness along the slide can be achieved with good guidance on both sides.
  • a particularly simple and detachable fastening results if the first housing part is fastened to the second housing part by means of screws.
  • the object is also achieved by a coolant circuit in which the main inlet and the main outlet of the coolant pump are fluidly connected to the main coolant circuit, the second secondary outlet being fluidly connected to the main coolant circuit via the secondary coolant line.
  • a control device such as a switching valve or thermostat, can advantageously be provided in the secondary coolant line.
  • the second secondary inlet can be connected to the main coolant circuit via a second secondary coolant line.
  • the coolant pump arrangement 2 consists of a housing assembly 4 in which a main pump 6 and a secondary pump 8, which is designed as a side channel pump, are provided.
  • the housing assembly 4 has an outer housing 10 in which a spiral delivery channel 12 is formed, into which a coolant is sucked in via an axial main inlet 14 also formed in the outer housing 10, which coolant is conveyed via the delivery channel 12 to a tangential main outlet 16 formed in the outer housing 10 and in a main coolant circuit 116 of the internal combustion engine 118 is promoted (see here Figure 4 ).
  • This outer housing 10 can in particular be formed by a cylinder crankcase, which has a recess for receiving the rest of the coolant pump.
  • a coolant pump impeller 20 is fastened radially inside the delivery channel 12 on a drive shaft 18, which is designed as a radial pump wheel, by the rotation of which the coolant is delivered in the delivery channel 12.
  • the coolant pump impeller 20 is driven by a belt 22 which drives a belt wheel 24 which is fastened to the axial end of the drive shaft 18 opposite the coolant pump impeller 20.
  • the belt wheel 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 in 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 on 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 concentrically to 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 volume flow control.
  • a side channel pump impeller 46 is formed on the axial side of the coolant pump impeller 20 opposite the main inlet 14 in one piece with the coolant pump impeller 20 and is accordingly driven with the coolant pump impeller 20.
  • This side channel pump impeller 46 has blades 48, which are arranged axially opposite to one as a side channel 50, which is formed in the first inner housing part 40, from which the annular projection 38 for mounting the control slide 28 to the coolant pump impeller is also located in the radially inner region 20 opposite side extends axially.
  • a secondary inlet 52, a secondary outlet 54 and a second secondary outlet 56 are formed in this first housing part 40, so that the side channel pump impeller 46 with the axially opposite side channel 50 forms the side channel pump 8, via which the pressure of the coolant from the secondary inlet 52 to the secondary outlet 54 of the side channel pump 8 is increased.
  • the second secondary outlet 56 is, as in particular below Figure 4 is described, fluidly connected to an auxiliary coolant line 124.
  • the coolant delivered by the side channel pump 8, which generates a hydraulic pressure, can now either be supplied to a first pressure chamber 58, which is located on the side of the control slide valve 28 facing away from the coolant pump impeller 20 between the bottom 42 of the valve Control slide 28 and a connection surface 60 of a second housing part 62 is formed or can be returned to the coolant pump via a solenoid valve 66.
  • 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 acts as a 3/2-way solenoid valve is formed and has a connection to the pressure chamber 58, so that a flow cross-section 70 of a pressure channel 72 is regulated depending on the position of its closing body 68.
  • a connection channel 74 is provided for pressure regulation or control of the pressure in the pressure chamber 64, which serves as a fail-safe bore, since this provides a pressure in the pressure chamber 64 that is always greater than the suction pressure of the side channel pump 8.
  • This pressure channel 72 extends from the secondary outlet 54 of the side channel 50 of the side channel pump 8 initially 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 72 is formed, which can be closed and released by the closing body 68 of the solenoid valve 66. 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 to the side channel 50 via the connecting channel 74, which is formed in the first housing part 40, this connecting channel 74 extending from a region of the secondary 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 completely released by not energizing the solenoid valve 66, as a result of which the closing body 68 is displaced into its position closing the flow cross section 70 of the pressure channel 72 due to a spring force ,
  • the result of this is that no pressure is built up by the coolant in the first pressure chamber 58, but rather the coolant present in the pressure chamber 58 can flow out to the main inlet 14 of the coolant pump arrangement via the other flow connection of the solenoid valve 66, which is not shown and is released in this state.
  • the side channel pump 8 delivers against the closed flow cross-section 70 of the pressure channel 72 with a speed-dependent pressure curve, a corresponding pressure prevailing in the second pressure chamber 64 depending on the exact positioning of the connecting channel 74.
  • This increased pressure in the second pressure chamber 64 has the result that a pressure difference arises at the bottom 42 of the control slide 28, which leads to the control slide 28 being displaced into its position which frees the annular gap 30 and thus ensures maximum delivery of the coolant pump arrangement.
  • the control slide 28 correspondingly assumes the same position, so that maximum delivery of the coolant pump arrangement is ensured even in this limp-home mode, without the need for a return spring or another non-hydraulic force.
  • the coolant from the first pressure chamber 58 can flow away via a return channel, not shown, which extends from the solenoid valve 66 through the second housing part 62 and then along the drive shaft 18 inside the first housing part 40 and over a bore in the coolant pump impeller 20 leads to the main inlet 14 of the coolant pump assembly.
  • the solenoid valve 66 is energized, as a result of which the closing body 68 releases the flow cross-section 70 of the pressure channel 72 and the flow cross-section between the first pressure chamber 58 and the one not shown Return channel reduced or closed.
  • the pressure which arises at the secondary outlet 54 of the side channel pump 8 is also supplied through the pressure channel 72 to the first pressure chamber 58 in order to move the control slide 28 into the annular gap 30.
  • valve 66 If a controllable solenoid valve 66 is used, it is also possible to move the valve 66 into intermediate positions, whereby an equilibrium of forces can be achieved for each position of the control slide 28, so that a complete control of the flow cross section of the annular gap 30 is made possible.
  • the first housing part 40 is fastened directly to the second housing part 62.
  • first Housing part 40 with an annular projection 80 which extends with a reduced diameter from the annular projection 38 further into the end facing away from the coolant pump impeller, is pushed into a radially inner receiving opening 82 of the second housing part 62 until the first housing part 40 with its between the projections 38, 80 formed shoulder 84 abuts against the connection surface 60 of the second housing part 62.
  • first housing part 40 is fastened to the second housing part by means of screws 86.
  • a plurality of through bores 88 and threaded blind holes 90 opposite one another are formed in the first housing part.
  • the outer housing 10 has an opening 92 at its axial end opposite the main inlet 14, into which an annular projection 94 of the second housing part 62 is formed protrudes that the protrusion 94 abuts against the inner wall of the opening 92.
  • an axial groove 96 is formed, in which a sealing ring 98 is arranged, which is correspondingly pressed when the second housing part 62 is fastened to the outer housing 10, 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 of which continues with its end facing the coolant pump impeller 44 with a somewhat enlarged diameter.
  • a radial groove 104, 106 is formed on the inner circumference and on the outer circumference of the bottom 42, 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 direction outer area at one
  • the inner wall of the hollow cylindrical projection 94 of the second housing part 62, which projects into the opening 92 of the outer housing 10, is slidably mounted and guided in a correspondingly sealing manner.
  • the coolant pump arrangement described has an extremely compact design, but is simple and inexpensive to manufacture and assemble, since there are a small number of parts. Additional lines for the hydraulic connection of the side channel pump to the pressure chambers of the control slide can be dispensed with, since these can be formed as simple bores in the two inner housing parts over very short distances. Because the control slide is guided in the inner area on the housing part, which simultaneously forms and radially delimits the side channel, the control slide can be guided along this boundary wall with clearly defined play and consequently defined leakage. Due to the axially very short construction due to the one-piece impeller for the side channel pump and the actual coolant delivery pump, this is particularly suitable for arrangement directly in an opening in the crankcase.
  • FIG. 4 shows a schematic view of a coolant circuit 114 according to the invention.
  • the coolant pump arrangement 2 is connected to a main coolant flow of a main coolant circuit 116 via the main inlet 14 and the main outlet 16 of the main pump 6.
  • the coolant is opened from the coolant Main outlet 16 of the main pump 6 through the internal combustion engine 118 and in a known manner through an exhaust gas recirculation cooler 120 to the open main inlet 14 of the main pump 6.
  • the exhaust gas recirculation cooler 120 serves to cool the exhaust gas that is to be returned from the outlet of the internal combustion engine 118 to the inlet thereof.
  • an exhaust gas recirculation valve 122 is provided in a known manner.
  • the internal combustion engine 118 In particular in the starting phase of the internal combustion engine 118, that is to say in a cold operating state, cooling of the exhaust gas to be returned is not desired. Rather, the internal combustion engine 118 is to be brought to operating temperature more quickly by the recirculation of hot exhaust gas. For this purpose, as described above, the outlet 16 of the delivery channel 12 of the main pump 6 is closed.
  • the secondary coolant line 124 is provided according to the invention, which is fluidly connected to the second secondary outlet 56 of the coolant pump arrangement 2.
  • a switching valve 126 is provided, which closes the secondary coolant line 124 when the operating temperature of the internal combustion engine 118 is reached.
  • the secondary coolant line 124 is fluidly connected to the main coolant circuit 116, here in the exhaust gas recirculation cooler 120, for example. In the cold starting phase of the internal combustion engine 118, a circulation of the coolant can be ensured by the secondary coolant flow mixing with the main coolant flow and re-entering the main pump 6 via the main inlet 14.

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  • General Engineering & Computer Science (AREA)
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Description

Die Erfindung betrifft eine in Hauptanspruch 1 definierte Kühlmittelpumpenanordnung für den KFZ-Bereich, die einen Gehäuseverbund mit einer Hauptpumpe und einer als Seitenkanalpumpe ausgebildeten Nebenpumpe aufweist, mit einem Haupteinlass und einem Hauptauslass, die mit einem Hauptkühlmittelkreislauf fluidisch verbindbar sind, mit einer Antriebswelle, mit einem Kühlmittelpumpenlaufrad der Hauptpumpe, welches zumindest drehfest auf der Antriebswelle angeordnet ist und über welches Kühlmittel in einen das Kühlmittelpumpenlaufrad umgebenden Förderkanal förderbar ist, mit einem verstellbaren Regelschieber, über den ein Durchströmungsquerschnitt eines Ringspalts zwischen einem Austritt des Kühlmittelpumpenlaufrades und dem Förderkanal regelbar ist, mit einer Seitenkanalpumpe mit einem Seitenkanalpumpenlaufrad, welches auf der Antriebswelle zumindest drehfest angeordnet ist, mit einem Seitenkanal der Seitenkanalpumpe, in dem durch Drehung des Seitenkanalpumpenlaufrades ein Druck erzeugbar ist, wobei der Seitenkanal einen Nebeneinlass und mindestens einen Nebenauslass aufweist, mit einem Druckkanal, über welchen ein Nebenauslass des Seitenkanals mit einem ersten Druckraum des Regelschiebers fluidisch verbindbar ist, und mit einem Ventil, über welches ein Durchströmungsquerschnitt des Druckkanals verschließbar und freigebbar ist. Des Weiteren betrifft die Erfindung einen Kühlmittelkreislauf mit einer solchen Kühlmittelpumpenanordnung für eine flüssigkeitsgekühlte Verbrennungskraftmaschine.The invention relates to a coolant pump arrangement for the automotive sector, which has a housing assembly with a main pump and a secondary pump designed as a side channel pump, with a main inlet and a main outlet, which are fluidically connectable to a main coolant circuit, with a drive shaft, with a Coolant pump impeller of the main pump, which is arranged at least in a rotationally fixed manner on the drive shaft and via which coolant can be conveyed into a delivery channel surrounding the coolant pump impeller, with an adjustable control slide, via which a flow cross section of an annular gap between an outlet of the coolant pump impeller and the delivery channel can be regulated, with a side channel pump with a side channel pump impeller, which is at least rotatably arranged on the drive shaft, with a side channel of the side channel pump, in which a Dru by rotating the side channel pump impeller ck can be generated, the side channel having a side inlet and at least one side outlet, with a pressure channel, via which a side outlet of the side channel can be fluidly connected to a first pressure chamber of the control slide, and with a valve, via which a flow cross section of the pressure channel can be closed and released , Furthermore, the invention relates to a coolant circuit with such a coolant pump arrangement for a liquid-cooled internal combustion engine.

Derartige Kühlmittelpumpenanordnungen dienen beispielsweise in Verbrennungsmotoren zur Mengenregelung des geförderten Kühlmittels in einem Kühlmittelkreislauf, 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 pump arrangements are used, for example, in internal combustion engines to regulate the quantity of coolant delivered in a coolant circuit in order to prevent the internal combustion engine from overheating. These pumps are usually driven by a Belt or chain drive so that the coolant pump wheel is driven at the speed of the crankshaft or at 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 delivered must be adapted to the coolant requirements of the internal combustion engine or the motor vehicle. To avoid increased pollutant emissions and reduce fuel consumption, the engine's cold running phase should be shortened in particular. This is done, among other things, by throttling the coolant flow or completely switching it off during this phase.

Hierbei kann jedoch das Problem auftreten, dass sich das still stehende Kühlmittel, im abgeschlossenen Kühlmittelkreislauf lokal zu sehr erwärmt und zu sieden beginnt. Um dieses Problem zu beheben ist es aus der DE 101 61 851 A1 , Absatz 0022 bekannt neben einer Hauptpumpe für einen Hauptkühlmitttelstrom eine Zusatzpumpe vorzusehen, die während eines geschlossenen Hauptkühlmittelstrom den Kühlmittelkreislauf in Bewegung hält und somit ein Sieden des Kühlmittels verhindert.However, the problem can arise here that the stationary coolant locally heats up too much in the closed coolant circuit and begins to boil. To fix this problem it is out of the DE 101 61 851 A1 , Paragraph 0022 known to provide in addition to a main pump for a main coolant flow, an additional pump that keeps the coolant circuit in motion during a closed main coolant flow and thus prevents boiling of the coolant.

Eine solche Zusatzpumpe ist jedoch hinsichtlich des Einsatzes und der Montage teuer und vergrößert den benötigten Bauraum erheblich.However, such an additional pump is expensive in terms of use and assembly and considerably increases the installation space required.

Darüber hinaus sind zur Regelung der Kühlmittelmenge verschiedene Pumpenausführungen zur Versorgung des Kühlmittelkreislaufes bekannt geworden. Neben elektrisch angetriebenen Kühlmittelpumpenanordnungen sind Pumpenanordnungen 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.In addition, various pump designs for supplying the coolant circuit have become known for regulating the amount of coolant. In addition to electrically driven coolant pump arrangements, pump arrangements are known which can be coupled to or separated from their drive via couplings, in particular hydrodynamic couplings. A particularly cost-effective and simply constructed option for regulating the conveyed coolant flow is the use of an axially displaceable control slide, which is connected to the coolant pump impeller is pushed so that to reduce the coolant flow, the pump does not deliver into the surrounding delivery 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.These sliders are also regulated in different ways. In addition to a purely electrical adjustment, a hydraulic adjustment of the slide has proven itself. This usually takes place via an annular piston chamber, which is filled with a hydraulic fluid and whose piston is connected to the slide, so that when the space is filled, the slide is moved over the impeller. The slide is reset 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 reset the slide.

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 amount of coolant required to move the slide via additional delivery units, such as additional piston / cylinder units or to have to compress other hydraulic fluids for actuation, mechanically controllable coolant pumps are known, on the drive shaft of which 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.Such a coolant device with a side channel pump acting as a secondary pump is shown in FIG DE 10 2012 207 387 A1 known. In this pump there is a slide on the back of the pump, which can be moved via a pressure in an annular chamber and can be reset via a spring. This annular chamber is formed in a housing, which in turn is arranged on the rear of the slide and in which a first side channel of the side channel pump is also arranged, which is correspondingly opposite to the side channel pump impeller arranged on the shaft. A second side channel is formed in a further housing part on the side opposite the side channel pump impeller. A 3/2-way valve in this pump closes a pressure side of the side channel pump in a first position and connects a suction side of the pump to the cooling circuit and the slide, and in a second position the pressure side to the ring chamber of the slide and the suction side to the cooling circuit connected.

Es stellt sich daher die Aufgabe, eine Kühlmittelpumpenanordnung sowie einen Kühlmittelkreislauf für eine Verbrennungskraftmaschine bereit zu stellen, bei der die oben genannten Probleme auf günstige Art und Weise bei geringem Herstellungs- und Montageaufwand gelöst werden. Zudem soll eine derartige Kühlmittelpumpenanordnung einen möglichst geringen Bauraum beanspruchen.It is therefore the task of providing a coolant pump arrangement and a coolant circuit for an internal combustion engine, in which the above-mentioned problems are solved in a favorable manner with little manufacturing and assembly effort. In addition, such a coolant pump arrangement should take up as little installation space as possible.

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

Dadurch, dass der Seitenkanal einen zweiten Nebenauslass aufweist, der über eine Nebenkühlmittelleitung mit dem Hauptkühlmittelkreislauf verbindbar ist, wird eine sehr kompakte Pumpenanordnung geschaffen, die einerseits eine besonders einfache und effiziente Regelung des Hauptkühlmittelstroms ermöglicht und andererseits eine ständige Umwälzung des Kühlmittels zumindest in Teilbereichen des Kühlkreislaufs auch bei geschlossenem Hauptkühlmittelstrom gewährleistet. Zudem ist der benötigte Bauraum gering gehalten.The fact that the side channel has a second secondary outlet, which can be connected to the main coolant circuit via an auxiliary coolant line, creates a very compact pump arrangement which, on the one hand, enables particularly simple and efficient control of the main coolant flow and, on the other hand, constant circulation of the coolant, at least in some areas of the cooling circuit guaranteed even when the main coolant flow is closed. In addition, the space required is kept small.

Eine besonders kompakte Kühlmittelpumpenanordnung wird dadurch bereit gestellt, 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. 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.A particularly compact coolant pump arrangement is provided in that the coolant pump impeller is formed in one piece with the side channel pump impeller and the side channel is formed in a first housing part on which the control slide slides is led. In addition, there are no assembly steps to attach the impeller to the shaft. There is also no need to manufacture a component. The first housing part takes on both the function as a flow housing and as a bearing 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 dem 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.The blades of the side channel pump impeller are preferably formed on a rear side of the coolant pump impeller designed as a radial pump impeller and are arranged axially opposite the side channel. The purely axial alignment of the side channel for blading reduces the radial space required, since no radially outer overflow channel is required. Accordingly, a maximum pressure can be generated for the existing installation space.

In einer besonders vorteilhaften, kompakten Ausführungsform ist zwischen dem Nebeneinlass und dem Nebenauslass ein Verbindungskanal vom Seitenkanal in einen zweiten Druckraum vorgesehen, wobei der zweite Druckraum zwischen einem Boden des Regelschiebers und dem ersten Gehäuseteil, in dem der Seitenkanal angeordnet ist, ausgebildet. Hierbei ist in vorteilhafter Weise der Verbindungskanal als Bohrung ausgeführt.In a particularly advantageous, compact embodiment, a connecting channel from the side channel into a second pressure chamber is provided between the secondary inlet and the secondary outlet, the second pressure chamber being formed between a bottom of the control slide and the first housing part in which the side channel is arranged. In this case, the connecting channel is advantageously designed as a bore.

Es ist grundsätzlich möglich, dass der Seitenkanal einen zweiten Nebeneinlass aufweist.It is fundamentally possible for the side channel to have a second secondary inlet.

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, radially surrounds the side channel pump impeller and is radially surrounded by a radially outer peripheral wall of the control slide. This wall accordingly fills the gap between the slide and the rotating side channel pump impeller and thus between the pressure-generating coolant flow and the delivery flow of the main pump. This wall can also 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 accordingly enables the control slide to be mounted internally on the advantageously machined outer surface. This inner mounting of the control slide simplifies installation in a receiving opening of a cylinder crankcase, the inner surfaces of which then do not have to be machined. Furthermore, such an internal guide results in a very exact axial movement without fear of tilting or tilting of the control slide, since a sufficiently long guide surface is always available despite the small installation 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.The first pressure chamber is preferably formed on the axial side of the control slide facing away from the coolant pump impeller, and the first housing part delimits a second pressure chamber to a first axial side and the control slide to the opposite axial side. Accordingly, the control slide can be adjusted entirely via hydraulic forces, which are only supplied to the corresponding pressure chambers. Additional annular spaces or piston spaces do not have to be formed. Due to the limitation by the first housing part, the fluidic connection to the pressure chambers can be established 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.The annular projection of the first housing part preferably delimits the two pressure spaces radially inward. additional Seals in this area are accordingly not required. 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 have to be installed here either, but the first pressure chamber can also be fluidly connected directly to the side channel of the pump via the holes in the housing.

Vorteilhafterweise erstreckt sich der Druckkanal vom Nebenauslass 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.The pressure channel advantageously extends from the secondary outlet of the side channel pump through the first housing part and a second housing part into the first pressure chamber, the flow cross section controlled by the valve being formed in the second housing part. In addition to the complete formation of the connection and pressure channels for controlling the control slide, the control valve can also be arranged accordingly in the housing, so that additional connections to the valve are also omitted here.

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.The annular projection of the first housing part preferably has a shoulder at its axial end, from which the annular projection with a reduced diameter extends further axially into a corresponding receiving opening of the second housing part, to which the first housing part is fastened. Accordingly, there is a direct centering of the two housing parts relative to one another via the inner projection, as a result of which the reception and guidance of the control slide is improved. This can be manufactured with small tolerances, so that a high level of tightness along the slide can be achieved with good guidance on both sides.

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

Die Aufgabe wird ebenfalls gelöst durch einen Kühlmittelkreislauf bei dem der Haupteinlass und der Hauptauslass der Kühlmittelpumpe fluidisch mit dem Hauptkühlmittelkreislauf verbunden sind, wobei der zweite Nebenauslass fluidisch über die Nebenkühlmittelleitung mit dem Hauptkühlmittelkreislauf verbunden ist.The object is also achieved by a coolant circuit in which the main inlet and the main outlet of the coolant pump are fluidly connected to the main coolant circuit, the second secondary outlet being fluidly connected to the main coolant circuit via the secondary coolant line.

Vorteilhafterweise kann in der Nebenkühlmittelleitung eine Regeleinrichtung, wie zum Beispiel ein Schaltventil oder Thermostatvorgesehen sein.A control device, such as a switching valve or thermostat, can advantageously be provided in the secondary coolant line.

In einer besonderen Ausführungsform kann der zweite Nebeneinlass über eine zweite Nebenkühlmittelleitung mit dem Hauptkühlmittelkreislauf verbunden sein.In a special embodiment, the second secondary inlet can be connected to the main coolant circuit via a second secondary coolant line.

Ein Ausführungsbeispiel einer erfindungsgemäßen Kühlmittelpumpenanordnung und eines erfindungsgemäßen Kühlmittelkreislaufs für einen Verbrennungsmotor ist in den Figuren dargestellt und wird nachfolgend beschrieben. Der Schutzumfang der Erfindung ist ausschließlich durch die nachfolgenden Ansprüche bestimmt. 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 schematische Ansicht eines erfindungsgemäßen Kühlmittelkreislaufes.
An embodiment of a coolant pump arrangement according to the invention and a coolant circuit according to the invention for an internal combustion engine is shown in the figures and is described below. The scope of protection of the invention is determined exclusively by the following claims. Here shows:
  • Figure 1 a side view of a coolant pump according to the invention in a sectional view.
  • Figure 2 one too Figure 1 rotated side view of the coolant pump according to the invention in a sectional view.
  • Figure 3 a front view cut in the area of a side channel pump of the coolant pump, and
  • Figure 4 is a schematic view of a coolant circuit according to the invention.

Die erfindungsgemäße Kühlmittelpumpenanordnung 2 besteht aus einem Gehäuseverbund 4, in dem eine Hauptpumpe 6 und eine Nebenpumpe 8, die als Seitenkanalpumpe ausgeführt ist, vorgesehen sind. Der Gehäuseverbund 4 besitzt ein Außengehäuse 10, in dem ein spiralförmiger Förderkanal 12 ausgebildet ist, in den über einen ebenfalls im Außengehäuse 10 ausgebildeten axialen Haupteinlass 14 ein Kühlmittel angesaugt wird, welches über den Förderkanal 12 zu einem im Außengehäuse 10 ausgebildeten tangentialen Hauptauslass 16 und in einen Hauptkühlmittelkreislauf 116 der Verbrennungskraftmaschine 118 gefördert wird (siehe hierzu Figur 4). Dieses Außengehäuse 10 kann insbesondere durch ein Zylinderkurbelgehäuse gebildet sein, welches eine Ausnehmung zur Aufnahme der übrigen Kühlmittelpumpe aufweist.The coolant pump arrangement 2 according to the invention consists of a housing assembly 4 in which a main pump 6 and a secondary pump 8, which is designed as a side channel pump, are provided. The housing assembly 4 has an outer housing 10 in which a spiral delivery channel 12 is formed, into which a coolant is sucked in via an axial main inlet 14 also formed in the outer housing 10, which coolant is conveyed via the delivery channel 12 to a tangential main outlet 16 formed in the outer housing 10 and in a main coolant circuit 116 of the internal combustion engine 118 is promoted (see here Figure 4 ). This outer housing 10 can in particular be formed by a cylinder crankcase, which has a recess for receiving the rest of the 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 fastened radially inside the delivery channel 12 on a drive shaft 18, which is designed as a radial pump wheel, by the rotation of which the coolant is delivered in the delivery channel 12.

Der Antrieb des Kühlmittelpumpenlaufrades 20 erfolgt über einen Riemen 22, der ein Riemenrad 24 antreibt, 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 coolant pump impeller 20 is driven by a belt 22 which drives a belt wheel 24 which is fastened to the axial end of the drive shaft 18 opposite the coolant pump impeller 20. The belt wheel 24 is supported by a double row ball bearing 26. A drive via a chain drive would also be possible.

Um den von der Kühlmittelpumpenanordnung 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 arrangement, a control slide 28 is used, which is displaceable in 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 on 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 concentrically to 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 volume flow control.

Um diesen Regelschieber 28 betätigen zu können, ist erfindungsgemäß an der zum Haupteinlass 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 Nebeneinlass 52, ein Nebenauslass 54 und ein zweiter Nebenauslass 56 ausgebildet, so dass das Seitenkanalpumpenlaufrad 46 mit dem axial gegenüberliegenden Seitenkanal 50 die Seitenkanalpumpe 8 bildet, über welche der Druck des Kühlmittels vom Nebeneinlass 52 zum Nebenauslass 54 der Seitenkanalpumpe 8 erhöht wird. Der zweite Nebenauslass 56 ist, wie insbesondere unter Figur 4 beschrieben wird, mit einer Nebenkühlmittelleitung 124 fluidisch verbunden.In order to be able to actuate this control slide 28, a side channel pump impeller 46 is formed on the axial side of the coolant pump impeller 20 opposite the main inlet 14 in one piece with the coolant pump impeller 20 and is accordingly driven with the coolant pump impeller 20. This side channel pump impeller 46 has blades 48, which are arranged axially opposite to one as a side channel 50, which is formed in the first inner housing part 40, from which the annular projection 38 for mounting the control slide 28 to the coolant pump impeller is also located in the radially inner region 20 opposite side extends axially. A secondary inlet 52, a secondary outlet 54 and a second secondary outlet 56 are formed in this first housing part 40, so that the side channel pump impeller 46 with the axially opposite side channel 50 forms the side channel pump 8, via which the pressure of the coolant from the secondary inlet 52 to the secondary outlet 54 of the side channel pump 8 is increased. The second secondary outlet 56 is, as in particular below Figure 4 is described, fluidly connected to an auxiliary coolant line 124.

Das durch die Seitenkanalpumpe 8 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 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 8 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 8 ist.The coolant delivered by the side channel pump 8, which generates a hydraulic pressure, can now either be supplied to a first pressure chamber 58, which is located on the side of the control slide valve 28 facing away from the coolant pump impeller 20 between the bottom 42 of the valve Control slide 28 and a connection surface 60 of a second housing part 62 is formed or can be returned to the coolant pump via a solenoid valve 66. 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 control or regulate the pressures in the pressure chambers 58, 64 in a targeted manner by means of the conveyed coolant of the side channel pump 8, a receptacle 65 for the valve 66 is provided with respect to the pressure chamber 58 in the second housing part 62, which acts as a 3/2-way solenoid valve is formed and has a connection to the pressure chamber 58, so that a flow cross-section 70 of a pressure channel 72 is regulated depending on the position of its closing body 68. A connection channel 74 is provided for pressure regulation or control of the pressure in the pressure chamber 64, which serves as a fail-safe bore, since this provides a pressure in the pressure chamber 64 that is always greater than the suction pressure of the side channel pump 8.

Dieser Druckkanal 72 erstreckt sich vom Nebenauslass 54 des Seitenkanals 50 der Seitenkanalpumpe 8 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.This pressure channel 72 extends from the secondary outlet 54 of the side channel 50 of the side channel pump 8 initially 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 72 is formed, which can be closed and released by the closing body 68 of the solenoid valve 66. From this controllable flow cross section 70, the pressure channel 72 extends further into the first pressure chamber 58.

Der zweite Druckraum 64 ist über den Verbindungskanal 74, welcher im ersten Gehäuseteil 40 ausgebildet ist, mit dem Seitenkanal 50 verbunden, wobei dieser Verbindungskanal 74 von einem Bereich des Nebeneinlasses 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.The second pressure chamber 64 is connected to the side channel 50 via the connecting channel 74, which is formed in the first housing part 40, this connecting channel 74 extending from a region of the secondary 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 Haupteinlass 14 der Kühlmittelpumpenanordnung abströmen kann. Stattdessen fördert in diesem Zustand die Seitenkanalpumpe 8 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 Kühlmittelpumpenanordnung 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 Kühlmittelpumpenanordnung sichergestellt wird, ohne dass hierzu eine Rückstellfeder oder eine andere, nicht hydraulische Kraft notwendig wäre.If the coolant pump is to deliver a maximum amount of coolant during operation, the annular gap 30 at the outlet 32 of the coolant pump impeller 20 is completely released by not energizing the solenoid valve 66, as a result of which the closing body 68 is displaced into its position closing the flow cross section 70 of the pressure channel 72 due to a spring force , The result of this is that no pressure is built up by the coolant in the first pressure chamber 58, but rather the coolant present in the pressure chamber 58 can flow out to the main inlet 14 of the coolant pump arrangement via the other flow connection of the solenoid valve 66, which is not shown and is released in this state. Instead, in this state, the side channel pump 8 delivers against the closed flow cross-section 70 of the pressure channel 72 with a speed-dependent pressure curve, a corresponding pressure prevailing in the second pressure chamber 64 depending on the exact positioning of the connecting channel 74. This increased pressure in the second pressure chamber 64 has the result that a pressure difference arises at the bottom 42 of the control slide 28, which leads to the control slide 28 being displaced into its position which frees the annular gap 30 and thus ensures maximum delivery of the coolant pump arrangement. In the event of a failure of the electrical supply to the solenoid valve 66, the control slide 28 correspondingly assumes the same position, so that maximum delivery of the coolant pump arrangement is ensured even in this limp-home mode, without the need for a return spring or another non-hydraulic force.

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 Haupteinlass 14 der Kühlmittelpumpenanordnung führt.The coolant from the first pressure chamber 58 can flow away via a return channel, not shown, which extends from the solenoid valve 66 through the second housing part 62 and then along the drive shaft 18 inside the first housing part 40 and over a bore in the coolant pump impeller 20 leads to the main inlet 14 of the coolant pump assembly.

Wird ein reduzierter Kühlmittelstrom zum Kühlmittelkreislauf 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 Nebenauslass 54 der Seitenkanalpumpe 8 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 Kühlmittelkreislauf unterbrochen wird.If a reduced coolant flow to the coolant circuit is demanded by the engine control, as is the case, for example, during the cold running phase, the solenoid valve 66 is energized, as a result of which the closing body 68 releases the flow cross-section 70 of the pressure channel 72 and the flow cross-section between the first pressure chamber 58 and the one not shown Return channel reduced or closed. Correspondingly, the pressure which arises at the secondary outlet 54 of the side channel pump 8 is also supplied through the pressure channel 72 to the first pressure chamber 58 in order to move the control slide 28 into the annular gap 30. In this state, there is correspondingly a pressure difference opposite the other position of the solenoid valve 66 at the bottom 42 of the control slide 28, which leads to the control slide 28 being displaced into the annular gap 30 and thus the coolant flow in the coolant circuit being interrupted.

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 into intermediate positions, whereby an equilibrium of forces can be achieved for each position of the control slide 28, 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 sicherzustellen, 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 be able to ensure the compact design through the one-piece design of the coolant pump impeller 20 with the side duct pump impeller 46 and a tight connection of the duct sections of the pressure duct 72 or the return duct formed in the first housing part 40 and in the second housing part 62 and to ensure the low leakages via the control slide 28 and to ensure complete controllability, the first housing part 40 is fastened directly to the second housing part 62. This is done by the first Housing part 40 with an annular projection 80, which extends with a reduced diameter from the annular projection 38 further into the end facing away from the coolant pump impeller, is pushed into a radially inner receiving opening 82 of the second housing part 62 until the first housing part 40 with its between the projections 38, 80 formed shoulder 84 abuts against the connection surface 60 of the second housing part 62. In this position, the first housing part 40 is fastened to the second housing part by means of screws 86. For this purpose, a plurality of through bores 88 and threaded blind holes 90 opposite one another 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 Haupteinlass 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.To fasten the two housing parts 40, 62 to the outer housing 10 and, consequently, to arrange the control slide 28 in the outer housing 10, the outer housing 10 has an opening 92 at its axial end opposite the main inlet 14, into which an annular projection 94 of the second housing part 62 is formed protrudes that the protrusion 94 abuts against the inner wall of the opening 92. Radially outside of this hollow cylindrical projection 94, an axial groove 96 is formed, in which a sealing ring 98 is arranged, which is correspondingly pressed when the second housing part 62 is fastened to the outer housing 10, 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 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 of which continues with its end facing the coolant pump impeller 44 with a somewhat enlarged diameter. A radial groove 104, 106 is formed on the inner circumference and on the outer circumference of the bottom 42, 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 direction outer area at one The inner wall of the hollow cylindrical projection 94 of the second housing part 62, which projects into the opening 92 of the outer housing 10, is slidably mounted and guided in a correspondingly sealing manner.

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.After installation, only the rear piece of the drive shaft 18 and the rear part of the second housing part 62, in which the solenoid valve 66 is received and on which the ball bearing 26, which carries the pulley 24, is pressed, protrudes from the opening 92 of the outer housing 10. The drive shaft 18 extends centrally with the interposition of a seal 112 through the two housing parts 40, 62.

Die beschriebene Kühlmittelpumpenanordnung 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 besonders zur Anordnung direkt in einer Öffnung des Kurbelgehäuses.The coolant pump arrangement described has an extremely compact design, but is simple and inexpensive to manufacture and assemble, since there are a small number of parts. Additional lines for the hydraulic connection of the side channel pump to the pressure chambers of the control slide can be dispensed with, since these can be formed as simple bores in the two inner housing parts over very short distances. Because the control slide is guided in the inner area on the housing part, which simultaneously forms and radially delimits the side channel, the control slide can be guided along this boundary wall with clearly defined play and consequently defined leakage. Due to the axially very short construction due to the one-piece impeller for the side channel pump and the actual coolant delivery pump, this is particularly suitable for arrangement directly in an opening in the crankcase.

Figur 4 zeigt in einer schematischen Ansicht einen erfindungsgemäßen Kühlmittelkreislauf 114. Die Kühlmittelpumpenanordnung 2 ist über den Haupteinlass 14 und den Hauptauslass 16 der Hauptpumpe 6 mit einem Hauptkühlmittelstrom eines Hauptkühlmittelkreislaufes 116 verbunden. Hierzu wird in normalen Betriebssituationen, das heißt bei warmer Verbrennungskraftmaschine 118, das Kühlmittel vom geöffneten Hauptauslass 16 der Hauptpumpe 6 durch die Verbrennungskraftmaschine 118 und auf bekannte Weise durch einen Abgasrückführkühler 120 zum geöffneten Haupteinlass 14 der Hauptpumpe 6 geführt. Der Abgasrückführkühler 120 dient der Kühlung des vom Auslass der Verbrennungskraftmaschine 118 zum Einlass desselben zurück zu führenden Abgases. Hierzu ist auf bekannte Weise ein Abgasrückführventil 122 vorgesehen. Figure 4 shows a schematic view of a coolant circuit 114 according to the invention. The coolant pump arrangement 2 is connected to a main coolant flow of a main coolant circuit 116 via the main inlet 14 and the main outlet 16 of the main pump 6. For this purpose, in normal operating situations, that is to say when the internal combustion engine 118 is warm, the coolant is opened from the coolant Main outlet 16 of the main pump 6 through the internal combustion engine 118 and in a known manner through an exhaust gas recirculation cooler 120 to the open main inlet 14 of the main pump 6. The exhaust gas recirculation cooler 120 serves to cool the exhaust gas that is to be returned from the outlet of the internal combustion engine 118 to the inlet thereof. For this purpose, an exhaust gas recirculation valve 122 is provided in a known manner.

Insbesondere in der Startphase der Verbrennungskraftmaschine 118, das heißt, in kaltem Betriebszustand ist eine Kühlung des zurück zu führenden Abgases nicht gewollt. Vielmehr soll die Verbrennungskraftmaschine 118 durch die Rückführung von heißem Abgas schneller auf Betriebstemperatur gebracht werden. Hierzu wird, wie oben beschrieben, der Auslass 16 des Förderkanals 12 der Hauptpumpe 6 geschlossen.In particular in the starting phase of the internal combustion engine 118, that is to say in a cold operating state, cooling of the exhaust gas to be returned is not desired. Rather, the internal combustion engine 118 is to be brought to operating temperature more quickly by the recirculation of hot exhaust gas. For this purpose, as described above, the outlet 16 of the delivery channel 12 of the main pump 6 is closed.

Um nun zu verhindern, dass in dem geschlossenen Hauptkühlmittelkreislaufes 116 das Kühlmittel aufgrund der Erwärmung der Verbrennungskraftmaschine 118 zu sieden beginnt, ist erfindungsgemäß die Nebenkühlmittelleitung 124 vorgesehen, die mit dem zweiten Nebenauslass 56 der Kühlmittelpumpenanordnung 2 fluidisch verbunden ist. In dieser Nebenkühlmittelleitung 124 ist ein Schaltventil 126 vorgesehen, das die Nebenkühlmittelleitung 124 bei erreichter Betriebstemperatur der Verbrennungskraftmaschine 118 verschließt. Die Nebenkühlmittelleitung 124 ist mit dem Hauptkühlmittelkreislauf 116 fluidisch, hier zum Beispiel im Abgasrückführkühler 120, verbunden. In der kalten Startphase der Verbrennungskraftmaschine 118 kann hierdurch eine Zirkulation des Kühlmittels gewährleistet werden, indem der Nebenkühlmittelstrom sich mit dem Hauptkühlmittelstrom vermischt und über den Haupteinlass 14 wieder in die Hauptpumpe 6 eintritt.In order to prevent the coolant in the closed main coolant circuit 116 from boiling due to the heating of the internal combustion engine 118, the secondary coolant line 124 is provided according to the invention, which is fluidly connected to the second secondary outlet 56 of the coolant pump arrangement 2. In this secondary coolant line 124, a switching valve 126 is provided, which closes the secondary coolant line 124 when the operating temperature of the internal combustion engine 118 is reached. The secondary coolant line 124 is fluidly connected to the main coolant circuit 116, here in the exhaust gas recirculation cooler 120, for example. In the cold starting phase of the internal combustion engine 118, a circulation of the coolant can be ensured by the secondary coolant flow mixing with the main coolant flow and re-entering the main pump 6 via the main inlet 14.

Es sollte deutlich sein, dass der Schutzbereich nicht auf das beschriebene Ausführungsbeispiel begrenzt ist, sondern ausschließlich durch die nachfolgenden Ansprüche bestimmt ist. 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 protection is not limited to the exemplary embodiment described, but rather is exclusively determined by the following claims. For example, only a pressure chamber could be used and the control slide could be reset via a spring.

Claims (17)

  1. Coolant pump assembly for the automotive sector, comprising a housing assembly with a main pump (6) and an auxiliary pump (8) designed as a side channel pump,
    with a main inlet (14) and a main outlet (16) adapted to be fluidly connected to a main coolant circuit (118),
    with a drive shaft (18),
    with a coolant pump impeller (20) of the main pump (6), which is arranged on the drive shaft (18) at least for rotation therewith and via which coolant can be conveyed into a conveyor channel (12) surrounding the coolant pump impeller (20),
    with an adjustable control slide (28), via which a flow cross-section of an annular gap (30) between an outlet (32) of the coolant pump impeller (20) and the delivery channel (12) can be adjusted,
    with a side channel pump impeller (46) of the side channel pump (8), which is arranged on the drive shaft (18) is arranged at least for rotation therewith,
    with a side channel (50) of the side channel pump (8), in which by rotation d the side channel pump impeller (46), a pressure can be generated, wherein the side channel (50) has a secondary inlet (52) and at least one secondary outlet (54),
    with a pressure channel (72) through which the secondary outlet (54) of the side channel (50) can be fluidically connected with a first pressure chamber (58) of the control slide (28),
    with a valve (66) via which a flow cross section (70) of the pressure channel (72) can be closed and released,
    characterized in that the side channel (50) has a second secondary outlet (56) which is connected with the main cooling circuit (116) via a secondary coolant line (124).
  2. Coolant pump assembly for the automotive sector of claim 1, 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) on which the control slide (28) is guided in a sliding manner.
  3. Coolant pump assembly for the automotive sector of claim 2, 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 the side channel (50).
  4. Coolant pump assembly for the automotive sector of claim 2 or 3, characterized in that a connecting channel (74) from the side channel (50) into a second pressure chamber (64) is provided between the secondary inlet (52) and the secondary outlet (54), the second pressure chamber (64) being provided on a side of the control slide (28) facing the coolant pump impeller (20), wherein the second pressure chamber is formed between a bottom (42) of the control slide (28) and the first housing part (40) in which the side channel (50) is arranged.
  5. Coolant pump assembly for the automotive sector of claim 4, characterized in that the connecting channel (74) is designed as a bore.
  6. Coolant pump assembly for the automotive sector of one of the preceding claims, characterized in that the side channel (50) has a second secondary inlet.
  7. Coolant pump assembly for the automotive sector of claim 2, characterized in that a radially outer limiting 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 peripheral wall (44) of the control slide (28).
  8. Coolant pump assembly for the automotive sector of one of claims 2 to 5 or claim 7, 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).
  9. Coolant pump assembly for the automotive sector of 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).
  10. Coolant pump assembly for the automotive sector of claims 4 and 8, 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 assembly for the automotive sector of claims 8 or 10, characterized in that the pressure channel (72) extends through the annular projection (38) of the first housing part (40).
  12. Coolant pump assembly for the automotive sector of claim 7, characterized in that the pressure channel (72) extends from the secondary outlet (54) of the side channel pump (8) 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 the second housing part (62).
  13. Coolant pump assembly for the automotive sector of claim 12 in conjunction with one of claims 8, 10 or 11, 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 with reduced diameter in an axial direction into a corresponding receiving opening (82) of the second housing part (62) to which the first housing part (40) is fastened.
  14. Coolant pump assembly for the automotive sector of claim 12 or 13, characterized in that the first housing part (40) is fastened on the second housing part (62) by means of screws (86).
  15. Coolant circuit for a liquid-cooled internal combustion engine having a coolant pump arrangement according to one of the preceding claims, characterized in that the main inlet (14) and the main outlet (16) of the coolant pump arrangement (2) are fluidically connected to the main cooling circuit (116), wherein the second secondary outlet (56) is fluidically connected with the main coolant circuit (116) via the secondary coolant line (124).
  16. Coolant circuit for an internal combustion engine according to claim 15, characterized in that a control device (126), such as a switching valve, thermostat, is provided in the secondary coolant line (124).
  17. Coolant circuit for an internal combustion engine according to claim 6 and 15, characterized in that the second secondary inlet is connected to the main cooling circuit (116) via a second secondary coolant line.
EP17186282.4A 2016-09-06 2017-08-15 Coolant pump assembly for the automotive sector and a coolant circuit for a combustion engine Active EP3290713B1 (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102016116636.7A DE102016116636B4 (en) 2016-09-06 2016-09-06 Coolant pump for the automotive sector and a coolant circuit for an internal combustion engine

Publications (2)

Publication Number Publication Date
EP3290713A1 EP3290713A1 (en) 2018-03-07
EP3290713B1 true EP3290713B1 (en) 2020-02-19

Family

ID=59655914

Family Applications (1)

Application Number Title Priority Date Filing Date
EP17186282.4A Active EP3290713B1 (en) 2016-09-06 2017-08-15 Coolant pump assembly for the automotive sector and a coolant circuit for a combustion engine

Country Status (2)

Country Link
EP (1) EP3290713B1 (en)
DE (1) DE102016116636B4 (en)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP4067665A1 (en) * 2021-03-31 2022-10-05 Airtex Products, S.A.U. Variable coolant pumps
DE102023002980B3 (en) 2023-07-21 2024-10-10 Mercedes-Benz Group AG Pump for a motor vehicle and motor vehicle

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10161851A1 (en) 2001-12-15 2003-06-26 Daimler Chrysler Ag Cooling circuit of a liquid-cooled internal combustion engine
DE102008049204A1 (en) * 2008-09-27 2010-04-01 Man Nutzfahrzeuge Ag Cooling system for vehicles with liquid-cooled internal combustion engine
EP2455615B1 (en) * 2010-11-19 2017-08-16 MAHLE International GmbH Pump
DE102012207387A1 (en) 2011-07-27 2013-01-31 Mahle International Gmbh Cooling device for internal combustion engine in motor car, has pressure relief valve arranged over pressure side of secondary pump and inserted along direction of cooling circuit when reaching pre-defined pressure
DE102011090208A1 (en) * 2011-12-30 2013-07-04 Dr. Ing. H.C. F. Porsche Ag Water pump for coolant supply for internal combustion engine of motor vehicle, has pump wheel arranged between two housing sections on drive shaft, where sealing and controlling element is interrupted in circumferential direction
DE102015119095B4 (en) 2015-11-06 2019-03-21 Pierburg Gmbh Coolant pump for an internal combustion engine

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

Also Published As

Publication number Publication date
EP3290713A1 (en) 2018-03-07
DE102016116636A1 (en) 2018-03-08
DE102016116636B4 (en) 2019-08-14

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