EP3066343B1 - Magnetic pump for an uxiliary assembly of a vehicle and method of controlling a magnetic pump for an auxiliary assembly - Google Patents

Magnetic pump for an uxiliary assembly of a vehicle and method of controlling a magnetic pump for an auxiliary assembly Download PDF

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Publication number
EP3066343B1
EP3066343B1 EP14755616.1A EP14755616A EP3066343B1 EP 3066343 B1 EP3066343 B1 EP 3066343B1 EP 14755616 A EP14755616 A EP 14755616A EP 3066343 B1 EP3066343 B1 EP 3066343B1
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EP
European Patent Office
Prior art keywords
axial piston
armature
outlet
auxiliary assembly
piston part
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EP14755616.1A
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German (de)
French (fr)
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EP3066343A1 (en
Inventor
Andres Tönnesmann
Matthias Baden
Costantino Brunetti
Michael Sanders
Andreas Köster
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Pierburg GmbH
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Pierburg GmbH
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B17/00—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
    • F04B17/03—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors
    • F04B17/04—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors using solenoids
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B17/00—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
    • F04B17/03—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors
    • F04B17/04—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors using solenoids
    • F04B17/042—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors using solenoids the solenoid motor being separated from the fluid flow
    • F04B17/044—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors using solenoids the solenoid motor being separated from the fluid flow using solenoids directly actuating the piston
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/10—Valves; Arrangement of valves
    • F04B53/12—Valves; Arrangement of valves arranged in or on pistons
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/14—Pistons, piston-rods or piston-rod connections

Definitions

  • the invention relates to a magnetic pump for an auxiliary unit of a vehicle having an inlet and an outlet, an electromagnet having a translationally movable armature, a core, a coil and a yoke, an axial piston which is movable up and down in a cylinder, a first check valve, which is biased against the axial piston and a second check valve, which is biased against an outlet opening of the cylinder and a method for controlling a magnetic pump for an auxiliary unit of a motor vehicle, wherein a coupled to an armature of an electromagnet axial piston by an alternating energization of the Spool is moved up and down in a cylinder for conveying a fluid from the inlet to the outlet.
  • Such magnetic pumps are used, for example, to provide the pressure for the hydraulic adjustment of a valve spool of a coolant pump driven by a belt pulley, the volume flow of which can be regulated in this way.
  • an armature of the electromagnet and with this armature an axial piston, which has an axial through-hole, in a cylinder moves up and down in these pumps.
  • the through-bore is closed at its end facing the outlet by a check valve, which is also arranged in the cylinder.
  • the ejection movement takes place against another check valve which bears against an outlet of the cylinder.
  • an intermittent pumping by energization and Brobestromung or partial energization of the coil of the electromagnet arises.
  • Such an electric fluid pump is for example from the EP 0 288 216 A1 respectively.
  • Another solenoid pump or vibration tank pump is used in the WO 2011/029577 A1 disclosed.
  • the axial piston is made in two parts and has an axial through hole, wherein the first Axialkolbenteil connected to the armature or is integral with the armature and can be lifted from the second Axialkolbenteil, wherein in the lifted state via a gap between the two Axialkolben inconvenience between the inlet and the outlet is the fluidic connection, a flow through the pump and in particular a return flow from a to be filled by the pump pressure pressure chamber is possible without having to use an additionally controlled valve.
  • a fail-safe position for example, for the application of a controlled via a slider coolant pump is created.
  • a compression spring is arranged between the first Axialkolbenteil and the second Axialkolbenteil, which ensures that the armature is in its fully retracted position in case of failure of the electromagnet and on the other hand dampens the stop of the two Axialkolbenmaschine upon movement of the armature from this position.
  • the second Axialkolbenteil is due to the compressive force of a second compared to the first compression spring, stronger compression spring at full return of the armature against the stop and in the operating positions during pumping operation of the armature against the first Axialkolbenteil. This ensures that when moving from the fully retracted position of the armature first, the gap between the first Axialkolbenteil and the second Axialkolbenteil is closed and then the axial piston is displaced as a unit during the actual pumping movement.
  • the stopper is formed on a first insert housing part, whereby the production of the entire outlet housing is simplified.
  • the first check valve is biased by a first spring against the second Axialkolbenteil and is moved with this in the direction of the outlet and the second check valve is biased by a second spring against the outlet opening of the cylinder. So on the one hand, a sufficient pressure build-up in the ejection movement ensured and on the other hand allows subsequent filling of the cylinder in pumping operation.
  • the first Axialkolbenteil is advantageously connected via a bore in the armature to the armature, whereby the joint movement is ensured. Nevertheless, the structure and the assembly is easy, since the attachment can be made by screwing or pressing and only the first Axialkolbenteil must be performed.
  • the effective diameter of the second Axialkolbenteils is greater than the effective diameter of the first Axialkolbenteils.
  • the inlet and the outlet are arranged at axially opposite ends of the magnetic pump, wherein the armature is arranged on the side of the inlet and the check valves and the second Axialkolbenteil are arranged on the side of the outlet.
  • An advantageous embodiment of the invention provides that in a discharge housing, a second insert housing part is arranged, in which the cylinder is formed, in which the second Axialkolbenteil out and the first check valve is arranged, wherein the second check valve is loaded against an outlet opening of the cylinder, which opens into an outlet space, which opens into the outlet. This simplifies the production and delimitation of the individual hydraulic chambers in the outlet housing.
  • the spring of the first check valve is designed such that the first check valve follows the second Axialkolbenteil, when it moves in the direction of the inlet delayed. As a result, a sufficient filling of the cylinder for fluid delivery is ensured.
  • a transverse bore is formed in each of the first axial piston part and the core on the inlet side region.
  • shocks between the moving parts or from the movable parts to their stops thereby preventing that at the second Axialkolbenteil in the region of the stopper and / or in the Area of the system on the first Axialkolbenteil and / or between the armature and the core elastic damping elements are arranged.
  • an annular, directed to Einlegegeophuseteil recess is formed on the second Axialkolbenteil, which dips into an axial end of the cylinder when fully displaced in the direction of the outlet anchor.
  • This recess serves in the movement of the axial piston in the direction of the outlet as a hydraulic damping chamber, which prevents a collision of the second Axialkolbenteils on the cylinder wall.
  • annular recess on the side of the inlet to an inlet housing of the magnetic pump is formed, into which an annular inlet facing corresponding projection of the armature with complete recovery of the armature dips.
  • the annular recess serves as a hydraulic damping chamber.
  • the figure shows a side view of a magnetic pump according to the invention in a sectional view.
  • the magnetic pump shown in the figure has an electromagnet 10, which is composed of a wound on a bobbin 12 coil 14, a yoke 16, a yoke ring 18 and a core 20 and a movable armature 22.
  • an electromagnet 10 which is composed of a wound on a bobbin 12 coil 14, a yoke 16, a yoke ring 18 and a core 20 and a movable armature 22.
  • the armature 22 is pulled by the occurring magnetic forces in a known manner in the direction of the core 20.
  • the magnetic pump has an inlet housing 24, in which an inlet 26 is formed for a fluid, and an outlet housing 28, in which an outlet 30 for the fluid is formed and which is arranged on the inlet housing 24 axially opposite side of the electromagnet 10.
  • the armature 22 arranged adjacent to the inlet housing 24 has at its axial end facing the inlet housing 24 an annular projection 32 which, in the illustrated position of the armature 22, projects into a correspondingly shaped annular recess 34 in the inlet housing 24.
  • the armature 22 has a central axial bore 36 in which a first Axialkolbenteil 38 is fixed, which is arranged axially opposite to the inlet 26.
  • the first Axialkolbenteil 38 is mounted in a sliding bushing 39 which is fixed inside the core 20 and protrudes from the inlet housing 24 into the outlet housing 28.
  • the first Axialkolbenteil 38 has an axial through-bore 40 and at least one transverse bore 42 through which the inlet 26 of the magnetic pump with a space 44 between the armature 22 and the core 20 is fluidly connected.
  • An additional connection in this space is via a transverse bore 46 in the core 20th manufactured, which is arranged in a region in which the core 20 has a reduced compared to the surrounding bobbin 12 diameter.
  • an elastic damping element 48 is attached to the core 20 on its surface facing the armature 22.
  • the inlet housing 24 is attached with the interposition of a sealing ring 50 on the return ring 18, on the axially opposite side of a further sealing ring 52 is arranged, which seals a gap between the bobbin 12 and the return ring 18, so that no fluid can reach the coil 14.
  • the core 20 On the axially opposite side of the electromagnet 10, the core 20 has a radial extension 54, on the axially on both sides more sealing rings 56, 58 are arranged, on the one hand the gap to the outlet housing 28 which is secured to the core 20 and on the other hand the gap to the bobbin 12 seal.
  • the first Axialkolbenteil 38 At the end facing the outlet 30, the first Axialkolbenteil 38 a bowl-shaped extension 60, against which a prestressed compression spring 62 abuts, the opposite axial end abuts against a second Axialkolbenteil 64, the first Axialkolbenteil 38 facing end corresponding to the extension 60 of the first Axialkolbenteils 38 is formed and to which an elastic damping element 66 is arranged. In this position is located between the first Axialkolbenteil 38 and the second Axialkolbenteil 64, a gap 67.
  • a first Einlegegeophuseteil 68 is arranged with a radial constriction 70, through which the outlet housing 28 is divided into a piston chamber 72 and a gap 74.
  • the second axial piston part 64 bears against the radial constriction 70, which serves as a stop 76 for the second axial piston part 64, with a radial expansion surface 75.
  • the effective diameter of the first Axialkolbenteils 38 is smaller than that of the second Axialkolbenteils 64.
  • an elastic damping element 78 is arranged in the area of the stop 76 in turn.
  • At the end 30 facing the end of the second Axialkolbenteil 64 is hollow cylindrical and protrudes into a cylinder 82 in which the hollow cylindrical part of the second Axialkolbenteils 64 is guided and which is arranged radially within the gap 74.
  • a through hole 83 of the Axialkolbenteils 64 dominant closure body 84 of a first check valve 86 is biased by a first spring 88 of the check valve 86, the opposite end against a cylinder 82 axially delimiting 90th is present, which surrounds an outlet opening 92 of the cylinder 82.
  • a closure body 94 of a second check valve 96 which controls the outlet opening 92, is pretensioned against this constriction 90 via a spring 98, whose opposite end abuts against a surface surrounding the outlet 30 of the outlet housing 28.
  • a second insert housing part 100 is arranged, which forms the cylinder 82 and its axial boundary wall 102 facing the outlet 30 separates the space 74 from an outlet space 104, which leads to the outlet 30 and in which the second check valve 96 is arranged.
  • this boundary wall 102 in turn, at least one opening 106 is formed, via which there is a continuous fluidic connection between the intermediate space 74 and the outlet space 104.
  • a compression spring 108 which is stronger than the compression spring 62 and which surrounds the cylinder 82.
  • This compression spring 108 is supported with its first axial end against the intermediate wall 102 and with its other axial end against the extension surface 75 of the second Axialkolbenteils 64 so that it is loaded in the direction of the first Axialkolbenteils 38.
  • the inlet 26 is fluidically connected to the outlet 30 via the through-bore 40, the gap 67, the piston space 72, the openings 80, 106 of the inserts 68, 100 and the outlet space 104.
  • the height and duration of the partial energization is selected so that the force of the first compression spring 62 is overcome, so that the first Axialkolbenteil 38 abuts against the second Axialkolbenteil 64 and thus the gap 67 between the two Axialkolben constitution 38, 64 closed via the damping element 66 is, so that the two Axialkolbenmaschine 38, 64 move in operation as a unit.
  • the second stronger compression spring 108 is not compressed at Crystalbestromung because their force is greater than that of the electromagnet 10 at Generalbestromung.
  • the force acting on the armature 22 in the direction of the outlet 30 is greater than the sum of the counteracting forces, ie the spring forces of the springs 62, 108 and the possibly existing acting on the components hydraulic forces. Accordingly, the axial piston 38, 64 is moved as a unit in the direction of the outlet 30. With the axial piston 38, 64, the first check valve 86 is moved in the cylinder 82 toward the outlet 30, so that in the cylinder 82, a pressure builds up, which eventually causes the second check valve 96 opens against its spring force and fluid from the cylinder 82 in the outlet space 104 flows.
  • the axial piston 38, 64 moves as a unit in the direction of the inlet 26. Due to its inertia and the resulting in this movement in the now closed by the second check valve 96 cylinder 82 negative pressure follows the first check valve 86th the axial piston 38, 64 significantly delayed because its spring force for a permanent contact with the axial piston 38, 64 is not sufficient. During this movement, fluid is also sucked through the axial passage bore 40, 83 into the cylinder 82, thus flowing through the gap between the first check valve 86 and the axial piston 38, 64 into the cylinder 82.
  • Another hydraulic damping chamber becomes effective in the movement of the second Axialkolbenteils 64 in the direction of the outlet 30.
  • the radial extension surface 75 of the second Axialkolbenteils 64 is bent at its outer periphery in the direction of the cylinder 82 in such a way that between the hollow cylindrical part, which can be driven into the cylinder and this surface an annular recess 110 is formed. In this engages the inlet 26 facing the end of the cylinder 82 during the movement of the axial piston 38, 64 in the direction of the outlet 30, so that the existing fluid in the recess 110 can escape only through gaps and thus dampens the movement.
  • the magnetic pump according to the invention has a very low wear and provides a simple and quick pressure equalization between inlet and outlet. At the same time, with appropriate use of the magnetic pump, this function of the provision of the Ankers can also be used as a fail-safe function. Thus it can be dispensed with a separate valve.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Electromagnetic Pumps, Or The Like (AREA)

Description

Die Erfindung betrifft eine Magnetpumpe für ein Hilfsaggregat eines Fahrzeugs mit einem Einlass und einem Auslass, einem Elektromagneten, der einen translatorisch bewegbaren Anker, einen Kern, eine Spule und ein Joch aufweist, einem Axialkolben, der in einem Zylinder auf- und abbewegbar ist, einem ersten Rückschlagventil, welches gegen den Axialkolben vorgespannt ist und einem zweiten Rückschlagventil, welches gegen eine Auslassöffnung des Zylinders vorgespannt ist sowie ein Verfahren zur Steuerung einer Magnetpumpe für ein Hilfsaggregat eines Kraftfahrzeugs, bei dem ein mit einem Anker eines Elektromagneten gekoppelter Axialkolben durch eine wechselnde Bestromung der Spule in einem Zylinder zur Förderung eines Fluids vom Einlass zum Auslass auf und ab bewegt wird.The invention relates to a magnetic pump for an auxiliary unit of a vehicle having an inlet and an outlet, an electromagnet having a translationally movable armature, a core, a coil and a yoke, an axial piston which is movable up and down in a cylinder, a first check valve, which is biased against the axial piston and a second check valve, which is biased against an outlet opening of the cylinder and a method for controlling a magnetic pump for an auxiliary unit of a motor vehicle, wherein a coupled to an armature of an electromagnet axial piston by an alternating energization of the Spool is moved up and down in a cylinder for conveying a fluid from the inlet to the outlet.

Derartige Magnetpumpen werden beispielsweise zur Bereitstellung des Drucks zur hydraulischen Verstellung eines Ventilschiebers einer über eine Riemenscheibe angetriebener Kühlmittelpumpe verwendet, deren Volumenstrom auf diese Weise regelbar ist.Such magnetic pumps are used, for example, to provide the pressure for the hydraulic adjustment of a valve spool of a coolant pump driven by a belt pulley, the volume flow of which can be regulated in this way.

Durch wechselnde Bestromung der Spule wird bei diesen Pumpen ein Anker des Elektromagneten und mit diesem Anker ein Axialkolben, welcher eine axiale Durchgangsbohrung aufweist, in einem Zylinder auf- und ab bewegt. Die Durchgangsbohrung wird an ihrem zum Auslass gerichteten Ende durch ein Rückschlagventil, welches ebenfalls im Zylinder angeordnet ist, verschlossen. Die Ausstoßbewegung erfolgt gegen ein weiteres Rückschlagventil, welches gegen einen Auslass des Zylinders anliegt. Beim Rückstellen des Ventils erfolgt ein Füllen des Zylinders, da dessen Auslass durch das zweite Rückschlagventil verschlossen wird und das erste Rückschlagventil vom Axialkolben aufgrund des im Zylinder aufgrund der Rückwärtsbewegung entstehenden Unterdrucks abgehoben wird. Durch erneute Bestromung erfolgt ein erneutes Ausschieben des Fluids aus dem Zylinder. Entsprechend entsteht ein stoßweises Pumpen durch Bestromung und Nichtbestromung oder Teilbestromung der Spule des Elektromagneten.
Eine derartige elektrische Fluidpumpe ist beispielsweise aus der EP 0 288 216 A1 bzw. DE 10 2007 016 856 A1 bekannt. Um ein unerwünschtes Abbremsen des Kolbens beziehungsweise des Ankers durch die axiale Bewegung des Ankers und der hierdurch an den gegenüberliegenden axialen Enden des Ankers entstehenden Über- oder Unterdrücken, werden die beiden Räume vor und hinter dem Anker über axial verlaufende Nuten oder entsprechende Ausformungen der Führung oder des Ankers miteinander verbunden, so dass ein Druckausgleich stattfinden kann.
Eine andere Magnetpumpe oder Schwingankerpumpe wird in der WO 2011/029577 A1 offenbart. Bei dieser Pumpe ist der Axialkolben nicht fest mit dem Anker verbunden, sondern wird lediglich über eine Druckfeder gegen den Anker gedrückt. Auf diese Weise ist die Einheit aus Kolben und Anker kostengünstiger herstellbar, da ein Versatz der Führungen ausgeglichen werden kann.
Diese bekannten Magnetpumpen haben jedoch den Nachteil, dass keine fail-safe Funktion gegeben ist. Dies bedeutet beispielsweise für die Anwendung zur Verstellung eines Verstellringes einer Kühlmittelpumpe, dass bei durch den Verstellring geschlossener Kühlmittelpumpe und Ausfall der Magnetpumpe, der Druck in der Verstellkammer nur sehr langsam durch Leckagen über die Magnetpumpe abgebaut werden kann oder zusätzliche Ablassventile verwendet werden müssen. Andernfalls kann es beispielsweise bei der Verwendung an einer hydraulisch regelbaren mechanischen Kühlmittelpumpe zu einer Überhitzung des Verbrennungsmotors mit den entsprechenden Folgeschäden kommen.By alternating energization of the coil, an armature of the electromagnet and with this armature an axial piston, which has an axial through-hole, in a cylinder moves up and down in these pumps. The through-bore is closed at its end facing the outlet by a check valve, which is also arranged in the cylinder. The ejection movement takes place against another check valve which bears against an outlet of the cylinder. When the valve is reset, the cylinder is filled, since its outlet is closed by the second check valve and the first check valve is lifted off the axial piston due to the negative pressure arising in the cylinder due to the backward movement. By renewed energization is a new expulsion of the fluid from the cylinder. Accordingly, an intermittent pumping by energization and Nichtbestromung or partial energization of the coil of the electromagnet arises.
Such an electric fluid pump is for example from the EP 0 288 216 A1 respectively. DE 10 2007 016 856 A1 known. To an undesirable braking of the piston or the armature by the axial movement of the armature and thereby resulting at the opposite axial ends of the armature overpressure or suppression, the two spaces in front of and behind the armature via axially extending grooves or corresponding formations of the guide or of the armature connected to each other, so that a pressure equalization can take place.
Another solenoid pump or vibration tank pump is used in the WO 2011/029577 A1 disclosed. In this pump, the axial piston is not firmly connected to the armature, but is pressed only by a compression spring against the armature. In this way, the unit of piston and armature is less expensive to produce, since an offset of the guides can be compensated.
However, these known magnetic pumps have the disadvantage that no fail-safe function is given. This means, for example, for the application for adjusting an adjusting ring of a coolant pump that when closed by the adjusting ring coolant pump and failure of the magnetic pump, the pressure in the adjustment only very can be slowly degraded by leaks through the solenoid pump or additional drain valves must be used. Otherwise, for example, when used on a hydraulically controllable mechanical coolant pump, overheating of the internal combustion engine with the corresponding consequential damage may occur.

Es ist daher Aufgabe der Erfindung eine Magnetpumpe bereitzustellen, mit der bei Ausfall des Elektromagneten ein schneller Rückfluss durch die Pumpe ermöglicht werden kann, was am Beispiel der Kühlmittelpumpe zu einer Entlastung des Verstellrings und somit zu einer Maximalförderung der Kühlmittelpumpe führt. Auch soll auf zusätzlich angesteuerte Ventile zum Ablassen des Drucks verzichtet werden können.It is therefore an object of the invention to provide a magnetic pump, with the failure of the electromagnet, a quick return flow can be made possible by the pump, which leads to the example of the coolant pump to a relief of the adjusting ring and thus to a maximum promotion of the coolant pump. It should also be possible to dispense with additionally controlled valves for releasing the pressure.

Diese Aufgabe wird durch eine Magnetpumpe mit den Merkmalen des Hauptanspruchs 1 sowie ein Verfahren mit den Merkmalen des Hauptanspruchs 17 gelöst.This object is achieved by a magnetic pump with the features of the main claim 1 and a method having the features of the main claim 17.

Dadurch, dass der Axialkolben zweiteilig ausgeführt ist und eine axiale Durchgangsbohrung aufweist, wobei der erste Axialkolbenteil mit dem Anker verbunden oder einteilig mit dem Anker ausgeführt ist und vom zweiten Axialkolbenteil abhebbar ist, wobei im abgehobenen Zustand über einen Spalt zwischen den beiden Axialkolbenteilen zwischen dem Einlass und dem Auslass die fluidische Verbindung besteht, wird eine Durchströmung der Pumpe und insbesondere eine Rückströmung aus einem durch den Pumpendruck zu befüllenden Druckraum möglich, ohne ein zusätzlich angesteuertes Ventil verwenden zu müssen. Somit wird eine fail-safe Position beispielsweise für den Anwendungsfall einer über einen Schieber geregelten Kühlmittelpumpe geschaffen. Dies wird auch durch ein Verfahren ermöglicht, bei dem bei Nichtbestromung der Spule der Anker in seine vollständig zurückgezogene Position gedrückt wird, in der durch den Anker oder den mit ihm verbundenen oder einstückig mit ihm ausgebildeten Axialkolben in dieser Position des Ankers kontinuierlich ein Spalt freigegeben wird, über den eine fluidische Verbindung zwischen dem Einlass und dem Auslass hergestellt wird.Characterized in that the axial piston is made in two parts and has an axial through hole, wherein the first Axialkolbenteil connected to the armature or is integral with the armature and can be lifted from the second Axialkolbenteil, wherein in the lifted state via a gap between the two Axialkolbenteilen between the inlet and the outlet is the fluidic connection, a flow through the pump and in particular a return flow from a to be filled by the pump pressure pressure chamber is possible without having to use an additionally controlled valve. Thus, a fail-safe position, for example, for the application of a controlled via a slider coolant pump is created. This is also made possible by a method in which, when the coil is not energized, the armature is pushed into its fully retracted position, in or through the armature or its associated with or integral with it formed axial piston in this position of the armature continuously a gap is released, via which a fluidic connection between the inlet and the outlet is made.

Vorzugsweise ist zwischen dem ersten Axialkolbenteil und dem zweiten Axialkolbenteil eine Druckfeder angeordnet, die bei Ausfall des Elektromagneten dafür sorgt, dass der Anker in seine vollständig zurückgezogene Position gedrückt wird und andererseits bei Bewegung des Ankers aus dieser Stellung den Anschlag der beiden Axialkolbenteile dämpft.Preferably, a compression spring is arranged between the first Axialkolbenteil and the second Axialkolbenteil, which ensures that the armature is in its fully retracted position in case of failure of the electromagnet and on the other hand dampens the stop of the two Axialkolbenteile upon movement of the armature from this position.

In einer vorteilhaften Ausführung liegt der zweite Axialkolbenteil aufgrund der Druckkraft einer im Vergleich zur ersten Druckfeder zweiten, stärkeren Druckfeder bei vollständiger Rückstellung des Ankers gegen den Anschlag an und in den Betriebsstellungen beim Pumpbetrieb des Ankers gegen den ersten Axialkolbenteil an. Hierdurch wird sichergestellt, dass bei Bewegung aus der vollständig zurückgezogenen Position des Ankers zunächst der Spalt zwischen dem ersten Axialkolbenteil und dem zweiten Axialkolbenteil geschlossen wird und anschließend der Axialkolben als Einheit während der eigentlichen Pumpbewegung verschoben wird.In an advantageous embodiment, the second Axialkolbenteil is due to the compressive force of a second compared to the first compression spring, stronger compression spring at full return of the armature against the stop and in the operating positions during pumping operation of the armature against the first Axialkolbenteil. This ensures that when moving from the fully retracted position of the armature first, the gap between the first Axialkolbenteil and the second Axialkolbenteil is closed and then the axial piston is displaced as a unit during the actual pumping movement.

Vorzugsweise ist der Anschlag an einem ersten Einlegegehäuseteil ausgebildet, wodurch die Herstellung des gesamten Auslassgehäuses vereinfacht wird.Preferably, the stopper is formed on a first insert housing part, whereby the production of the entire outlet housing is simplified.

Das erste Rückschlagventil ist über eine erste Feder gegen den zweiten Axialkolbenteil vorgespannt und wird mit diesem in Richtung des Auslasses bewegt und das zweite Rückschlagventil ist über eine zweite Feder gegen die Auslassöffnung des Zylinders vorgespannt. So wird einerseits ein ausreichender Druckaufbau bei der Ausstoßbewegung sichergestellt und andererseits ein anschließendes Füllen des Zylinders im Pumpbetrieb ermöglicht.The first check valve is biased by a first spring against the second Axialkolbenteil and is moved with this in the direction of the outlet and the second check valve is biased by a second spring against the outlet opening of the cylinder. So on the one hand, a sufficient pressure build-up in the ejection movement ensured and on the other hand allows subsequent filling of the cylinder in pumping operation.

Der erste Axialkolbenteil ist vorteilhaft über eine Bohrung im Anker mit dem Anker verbunden, wodurch die gemeinsame Bewegung sichergestellt wird. Dennoch ist der Aufbau und die Montage einfach, da die Befestigung durch Schrauben oder Pressen hergestellt werden kann und lediglich der erste Axialkolbenteil geführt werden muss.The first Axialkolbenteil is advantageously connected via a bore in the armature to the armature, whereby the joint movement is ensured. Nevertheless, the structure and the assembly is easy, since the attachment can be made by screwing or pressing and only the first Axialkolbenteil must be performed.

Vorzugsweise ist der wirksame Durchmesser des zweiten Axialkolbenteils größer als der wirksame Durchmesser des ersten Axialkolbenteils. Hierdurch wird eine Füllung des Kolbenraums beim Ausstoß des Fluids durch einen Teil des geförderten Fluids sichergestellt, so dass Druckunterschiede innerhalb der Pumpenkammern ausgeglichen werden.Preferably, the effective diameter of the second Axialkolbenteils is greater than the effective diameter of the first Axialkolbenteils. As a result, a filling of the piston chamber during the discharge of the fluid is ensured by a portion of the delivered fluid, so that pressure differences within the pump chambers are compensated.

In einer bevorzugten Ausbildung der Erfindung sind der Einlass und der Auslass an axial gegenüberliegenden Enden der Magnetpumpe angeordnet, wobei der Anker an der Seite des Einlasses angeordnet ist und die Rückschlagventile und der zweite Axialkolbenteil an der Seite des Auslasses angeordnet sind. Es ergibt sich eine axiale Durchströmung der Pumpe mit geringen Pumpverlusten und der Möglichkeit hydraulische Dämpfungskammern zu schaffen.In a preferred embodiment of the invention, the inlet and the outlet are arranged at axially opposite ends of the magnetic pump, wherein the armature is arranged on the side of the inlet and the check valves and the second Axialkolbenteil are arranged on the side of the outlet. The result is an axial flow through the pump with low pumping losses and the ability to create hydraulic damping chambers.

Eine vorteilhafte Ausbildung der Erfindung sieht vor, dass in einem Auslassgehäuse ein zweites Einlegegehäuseteil angeordnet ist, in dem der Zylinder ausgebildet ist, in welchem der zweite Axialkolbenteil geführt und das erste Rückschlagventil angeordnet ist, wobei das zweite Rückschlagventil gegen eine Auslassöffnung des Zylinders belastet ist, die in einen Auslassraum mündet, der in den Auslass mündet. Dies vereinfacht die Herstellung und Abgrenzung der einzelnen hydraulischen Kammern im Auslassgehäuse.An advantageous embodiment of the invention provides that in a discharge housing, a second insert housing part is arranged, in which the cylinder is formed, in which the second Axialkolbenteil out and the first check valve is arranged, wherein the second check valve is loaded against an outlet opening of the cylinder, which opens into an outlet space, which opens into the outlet. This simplifies the production and delimitation of the individual hydraulic chambers in the outlet housing.

Vorzugsweise besteht eine kontinuierliche fluidische Verbindung zwischen einem Kolbenraum, in welchen der erste Axialkolbenteil ragt, einem Zwischenraum, der den Zylinder umgibt, und dem Auslassraum. Dies führt zu relativ geringen notwendigen Stellkräften des Elektromagneten, da ein Druckausgleich zwischen den Kammern hergestellt werden kann. Auch ermöglicht dies die Herstellung der fluidischen Verbindung zwischen dem Einlass und dem Auslass.Preferably, there is a continuous fluidic connection between a piston space in which the first Axialkolbenteil protrudes, a gap surrounding the cylinder, and the outlet space. This leads to relatively small necessary restoring forces of the electromagnet, since a pressure equalization between the chambers can be produced. Also, this allows the fluidic connection to be established between the inlet and the outlet.

Dabei besteht die fluidische Verbindung über Öffnungen im zweiten Einlegegehäuseteil und im ersten Einlegegehäuseteil, an dem der zwischen dem Zwischenraum und dem Kolbenraum angeordnete Anschlag ausgebildet ist. So können die hydraulischen Kammern und deren Verbindungen zueinander, der Anschlag und die Führung des zweiten Axialkolbenteils auf einfache Weise hergestellt werden.In this case, the fluidic connection via openings in the second insert housing part and in the first insert housing part, on which the arranged between the intermediate space and the piston chamber stop is formed. Thus, the hydraulic chambers and their connections to each other, the stop and the guide of the second Axialkolbenteils can be made in a simple manner.

In einer weiterführenden Ausführung ist die Feder des ersten Rückschlagventils derart ausgelegt, dass das erste Rückschlagventil dem zweiten Axialkolbenteil, bei dessen Bewegung in Richtung des Einlasses verzögert folgt. Hierdurch wird eine ausreichende Füllung des Zylinders zur Fluidförderung sichergestellt.In a further embodiment, the spring of the first check valve is designed such that the first check valve follows the second Axialkolbenteil, when it moves in the direction of the inlet delayed. As a result, a sufficient filling of the cylinder for fluid delivery is ensured.

Um eine Dämpfung der Bewegung des Ankers beziehungsweise des Axialkolbens durch Kompression des Fluids im Raum zwischen dem Anker und dem Kern zu verringern, ist im ersten Axialkolbenteil und am Kern am einlassseitigen Bereich jeweils eine Querbohrung ausgebildet.In order to reduce damping of the movement of the armature or of the axial piston by compression of the fluid in the space between the armature and the core, a transverse bore is formed in each of the first axial piston part and the core on the inlet side region.

Des Weiteren werden Stöße zwischen den sich bewegenden Teilen oder von den bewegbaren Teilen zu ihren Anschlägen, dadurch verhindert, dass am zweiten Axialkolbenteil im Bereich des Anschlags und/oder im Bereich der Anlage am ersten Axialkolbenteil und/oder zwischen dem Anker und dem Kern elastische Dämpfungselemente angeordnet sind.Furthermore, shocks between the moving parts or from the movable parts to their stops, thereby preventing that at the second Axialkolbenteil in the region of the stopper and / or in the Area of the system on the first Axialkolbenteil and / or between the armature and the core elastic damping elements are arranged.

In einer Weiterbildung der Erfindung ist am zweiten Axialkolbenteil eine ringförmige, zum Einlegegehäuseteil gerichtete Ausnehmung ausgebildet, die in ein axiales Ende des Zylinders bei vollständig in Richtung des Auslasses verstellten Anker eintaucht. Diese Ausnehmung dient bei der Bewegung des Axialkolbens in Richtung des Auslasses als hydraulische Dämpfungskammer, die einen Stoß des zweiten Axialkolbenteils an der Zylinderwand verhindert.In a further development of the invention, an annular, directed to Einlegegehäuseteil recess is formed on the second Axialkolbenteil, which dips into an axial end of the cylinder when fully displaced in the direction of the outlet anchor. This recess serves in the movement of the axial piston in the direction of the outlet as a hydraulic damping chamber, which prevents a collision of the second Axialkolbenteils on the cylinder wall.

In gleicher Weise wird ein Stoß bei der Bewegung des Ankers in Richtung des Einlasses verhindert, indem an der Seite des Einlasses eine ringförmige Ausnehmung an einem Einlassgehäuse der Magnetpumpe ausgebildet ist, in die ein ringförmiger zum Einlass weisender korrespondierender Vorsprung des Ankers bei vollständiger Rückstellung des Ankers eintaucht. Auch hier dient die ringförmige Ausnehmung als hydraulische Dämpfungskammer.Similarly, a shock in the movement of the armature is prevented in the direction of the inlet by an annular recess on the side of the inlet to an inlet housing of the magnetic pump is formed, into which an annular inlet facing corresponding projection of the armature with complete recovery of the armature dips. Again, the annular recess serves as a hydraulic damping chamber.

Es wird somit eine Magnetpumpe geschaffen, die bei Ausfall des Elektromagneten oder dessen Bestromung eine fail-safe Position aufweist, in der die Pumpe in beide Richtungen frei durchströmt werden kann. So kann auf ein zusätzliches Absperrventil verzichtet werden. Selbstverständlich kann diese Position auch bewusst zum Öffnen der Verbindung angefahren werden. Stöße durch die Bewegung des Axialkolbens beziehungsweise des Ankers werden zuverlässig vermieden. Gleichzeitig wird ein unerwünschter hydraulischer Gegendruck, der eine erhöhte Magnetkraft erfordern würde, verhindert.It is thus created a magnetic pump, which has a fail-safe position in case of failure of the electromagnet or its energization, in which the pump can be freely flowed through in both directions. So can be dispensed with an additional shut-off valve. Of course, this position can also be approached deliberately to open the connection. Impacts caused by the movement of the axial piston or the armature are reliably avoided. At the same time, an undesirable hydraulic back pressure that would require increased magnetic force is prevented.

Ein Ausführungsbeispiel einer erfindungsgemäßen Magnetpumpe ist in der Figur dargestellt und wird nachfolgend beschrieben.An embodiment of a magnetic pump according to the invention is shown in the figure and will be described below.

Die Figur zeigt eine Seitenansicht einer erfindungsgemäßen Magnetpumpe in geschnittener Darstellung.The figure shows a side view of a magnetic pump according to the invention in a sectional view.

Die in der Figur dargestellte Magnetpumpe weist einen Elektromagneten 10 auf, der sich aus einer auf einen Spulenträger 12 gewickelten Spule 14, einem Joch 16, einem Rückschlussring 18 sowie einem Kern 20 und einem beweglichen Anker 22 zusammensetzt. Durch Bestromen der Spule 14 wird der Anker 22 durch die auftretenden magnetischen Kräfte in bekannter Weise in Richtung des Kerns 20 gezogen.The magnetic pump shown in the figure has an electromagnet 10, which is composed of a wound on a bobbin 12 coil 14, a yoke 16, a yoke ring 18 and a core 20 and a movable armature 22. By energizing the coil 14, the armature 22 is pulled by the occurring magnetic forces in a known manner in the direction of the core 20.

Die Magnetpumpe weist ein Einlassgehäuse 24, in dem ein Einlass 26 für ein Fluid ausgebildet ist, und ein Auslassgehäuse 28 auf, in dem ein Auslass 30 für das Fluid ausgebildet ist und welches an der zum Einlassgehäuse 24 axial gegenüberliegenden Seite des Elektromagneten 10 angeordnet ist. Der benachbart zum Einlassgehäuse 24 angeordnete Anker 22 weist an seinem zum Einlassgehäuse 24 weisenden axialen Ende einen ringförmigen Vorsprung 32 auf, der in der dargestellten Position des Ankers 22 in eine korrespondierend geformte ringförmige Ausnehmung 34 im Einlassgehäuse 24 ragt. Des Weiteren weist der Anker 22 eine zentrale axiale Bohrung 36 auf, in welcher ein erster Axialkolbenteil 38 befestigt ist, der axial gegenüberliegend zum Einlass 26 angeordnet ist.The magnetic pump has an inlet housing 24, in which an inlet 26 is formed for a fluid, and an outlet housing 28, in which an outlet 30 for the fluid is formed and which is arranged on the inlet housing 24 axially opposite side of the electromagnet 10. The armature 22 arranged adjacent to the inlet housing 24 has at its axial end facing the inlet housing 24 an annular projection 32 which, in the illustrated position of the armature 22, projects into a correspondingly shaped annular recess 34 in the inlet housing 24. Furthermore, the armature 22 has a central axial bore 36 in which a first Axialkolbenteil 38 is fixed, which is arranged axially opposite to the inlet 26.

Der erste Axialkolbenteil 38 ist in einer Gleitbuchse 39 gelagert, die im Innern des Kerns 20 befestigt ist und ragt vom Einlassgehäuse 24 bis in das Auslassgehäuse 28. Der erste Axialkolbenteil 38 weist eine axiale Durchgangsbohrung 40 sowie mindestens eine Querbohrung 42 auf, über die der Einlass 26 der Magnetpumpe mit einem Raum 44 zwischen dem Anker 22 und dem Kern 20 fluidisch verbunden ist. Eine zusätzliche Verbindung in diesen Raum wird über eine Querbohrung 46 im Kern 20 hergestellt, die in einem Bereich angeordnet ist, in dem der Kern 20 einen im Vergleich zum umgebenden Spulenträger 12 verringerten Durchmesser aufweist. Des Weiteren ist am Kern 20 an seiner zum Anker 22 weisenden Oberfläche ein elastisches Dämpfungselement 48 befestigt. Das Einlassgehäuse 24 ist unter Zwischenlage eines Dichtrings 50 am Rückschlussring 18 befestigt, an dessen axial gegenüberliegender Seite ein weiterer Dichtring 52 angeordnet ist, die einen Spalt zwischen dem Spulenträger 12 und dem Rückschlussring 18 abdichtet, so dass kein Fluid zur Spule 14 gelangen kann. Auf der axial gegenüberliegende Seite des Elektromagneten 10 weist der Kern 20 eine radiale Erweiterung 54 auf, an der axial beidseitig weitere Dichtringe 56, 58 angeordnet sind, die einerseits den Spalt zum Auslassgehäuse 28, welches am Kern 20 befestigt ist und anderseits den Spalt zum Spulenträger 12 abdichten.The first Axialkolbenteil 38 is mounted in a sliding bushing 39 which is fixed inside the core 20 and protrudes from the inlet housing 24 into the outlet housing 28. The first Axialkolbenteil 38 has an axial through-bore 40 and at least one transverse bore 42 through which the inlet 26 of the magnetic pump with a space 44 between the armature 22 and the core 20 is fluidly connected. An additional connection in this space is via a transverse bore 46 in the core 20th manufactured, which is arranged in a region in which the core 20 has a reduced compared to the surrounding bobbin 12 diameter. Furthermore, an elastic damping element 48 is attached to the core 20 on its surface facing the armature 22. The inlet housing 24 is attached with the interposition of a sealing ring 50 on the return ring 18, on the axially opposite side of a further sealing ring 52 is arranged, which seals a gap between the bobbin 12 and the return ring 18, so that no fluid can reach the coil 14. On the axially opposite side of the electromagnet 10, the core 20 has a radial extension 54, on the axially on both sides more sealing rings 56, 58 are arranged, on the one hand the gap to the outlet housing 28 which is secured to the core 20 and on the other hand the gap to the bobbin 12 seal.

Am zum Auslass 30 weisenden Ende weist der erste Axialkolbenteil 38 eine schüsselförmige Erweiterung 60 auf, gegen die eine vorgespannte Druckfeder 62 anliegt, deren entgegengesetztes axiales Ende gegen einen zweiten Axialkolbenteil 64 anliegt, dessen zum ersten Axialkolbenteil 38 gewandtes Ende korrespondierend zur Erweiterung 60 des ersten Axialkolbenteils 38 ausgebildet ist und an dem ein elastisches Dämpfungselement 66 angeordnet ist. In dieser Position befindet sich zwischen dem ersten Axialkolbenteil 38 und dem zweiten Axialkolbenteil 64 ein Spalt 67. Im Auslassgehäuse 28 ist ein erstes Einlegegehäuseteil 68 mit einer radialen Einschnürung 70 angeordnet, durch die das Auslassgehäuse 28 in einen Kolbenraum 72 und einen Zwischenraum 74 unterteilt wird. In der in Figur 1 dargestellten Position liegt der zweite Axialkolbenteil 64 mit einer radialen Erweiterungsfläche 75 gegen die radiale Einschnürung 70, die als Anschlag 76 für den zweiten Axialkolbenteil 64 dient, an. Entsprechend ist der Wirkdurchmesser des ersten Axialkolbenteils 38 kleiner als der des zweiten Axialkolbenteils 64. Im Bereich des Anschlags 76 ist an der Erweiterungsfläche 75 wiederum ein elastisches Dämpfungselement 78 angeordnet. Über eine im ersten Einlegegehäuseteil 68 ausgebildete Öffnung 80 besteht eine kontinuierliche fluidische Verbindung des Kolbenraums 72, in den der erste Axialkolbenteil 38 ragt, zum Zwischenraum 74.At the end facing the outlet 30, the first Axialkolbenteil 38 a bowl-shaped extension 60, against which a prestressed compression spring 62 abuts, the opposite axial end abuts against a second Axialkolbenteil 64, the first Axialkolbenteil 38 facing end corresponding to the extension 60 of the first Axialkolbenteils 38 is formed and to which an elastic damping element 66 is arranged. In this position is located between the first Axialkolbenteil 38 and the second Axialkolbenteil 64, a gap 67. In the outlet housing 28, a first Einlegegehäuseteil 68 is arranged with a radial constriction 70, through which the outlet housing 28 is divided into a piston chamber 72 and a gap 74. In the in FIG. 1 In the position shown, the second axial piston part 64 bears against the radial constriction 70, which serves as a stop 76 for the second axial piston part 64, with a radial expansion surface 75. Accordingly, the effective diameter of the first Axialkolbenteils 38 is smaller than that of the second Axialkolbenteils 64. In the area of the stop 76 is on the extension surface 75 in turn an elastic damping element 78 is arranged. By way of an opening 80 formed in the first insert housing part 68, there is a continuous fluidic connection of the piston chamber 72 into which the first axial piston part 38 protrudes, to the intermediate space 74.

Am zum Auslass 30 weisenden Ende ist der zweite Axialkolbenteil 64 hohlzylinderförmig ausgebildet und ragt in einen Zylinder 82, in dem der hohlzylinderförmige Teil des zweiten Axialkolbenteils 64 geführt wird und der radial innerhalb des Zwischenraums 74 angeordnet ist. Gegen das offene, zum Auslass 30 weisende Ende des zweiten Axialkolbenteils 64 wird ein die Durchgangsbohrung 83 des Axialkolbenteils 64 beherrschender Verschlusskörper 84 eines ersten Rückschlagventils 86 mittels einer ersten Feder 88 des Rückschlagventils 86 vorgespannt, deren gegenüberliegende Ende gegen eine den Zylinder 82 axial begrenzende Einschnürung 90 anliegt, die eine Auslassöffnung 92 des Zylinders 82 umgibt.At the end 30 facing the end of the second Axialkolbenteil 64 is hollow cylindrical and protrudes into a cylinder 82 in which the hollow cylindrical part of the second Axialkolbenteils 64 is guided and which is arranged radially within the gap 74. Against the open, the outlet 30 facing end of the second Axialkolbenteils 64, a through hole 83 of the Axialkolbenteils 64 dominant closure body 84 of a first check valve 86 is biased by a first spring 88 of the check valve 86, the opposite end against a cylinder 82 axially delimiting 90th is present, which surrounds an outlet opening 92 of the cylinder 82.

Gegen diese Einschnürung 90 ist ein die Auslassöffnung 92 beherrschender Verschlusskörper 94 eines zweiten Rückschlagventils 96 über eine Feder 98 vorgespannt, deren gegenüberliegendes Ende gegen eine den Auslass 30 des Auslassgehäuses 28 umgebende Fläche anliegt. Im Auslassgehäuse 28 ist ein zweites Einlegegehäuseteil 100 angeordnet, welches den Zylinder 82 bildet und dessen axiale zum Auslass 30 weisende Begrenzungswand 102 den Zwischenraum 74 von einem Auslassraum 104 trennt, der zum Auslass 30 führt und in dem das zweite Rückschlagventil 96 angeordnet ist. In dieser Begrenzungswand 102 ist wiederum mindestens eine Öffnung 106 ausgebildet, über die eine kontinuierliche fluidische Verbindung zwischen dem Zwischenraum 74 und dem Auslassraum 104 besteht.A closure body 94 of a second check valve 96, which controls the outlet opening 92, is pretensioned against this constriction 90 via a spring 98, whose opposite end abuts against a surface surrounding the outlet 30 of the outlet housing 28. In the outlet housing 28, a second insert housing part 100 is arranged, which forms the cylinder 82 and its axial boundary wall 102 facing the outlet 30 separates the space 74 from an outlet space 104, which leads to the outlet 30 and in which the second check valve 96 is arranged. In this boundary wall 102, in turn, at least one opening 106 is formed, via which there is a continuous fluidic connection between the intermediate space 74 and the outlet space 104.

Zusätzlich befindet sich im Zwischenraum 74 eine Druckfeder 108, welche stärker ist als die Druckfeder 62, und die den Zylinder 82 umgibt. Diese Druckfeder 108 stützt sich mit ihrem ersten axialen Ende gegen die Zwischenwand 102 und mit ihrem anderen axialen Ende gegen die Erweiterungsfläche 75 des zweiten Axialkolbenteils 64 ab, so dass dieser in Richtung des ersten Axialkolbenteils 38 belastet wird.In addition, located in the intermediate space 74 is a compression spring 108 which is stronger than the compression spring 62 and which surrounds the cylinder 82. This compression spring 108 is supported with its first axial end against the intermediate wall 102 and with its other axial end against the extension surface 75 of the second Axialkolbenteils 64 so that it is loaded in the direction of the first Axialkolbenteils 38.

An diesem Ende des zweiten Axialkolbenteils ist eine weitere ringförmige in Axialrichtung sich erstreckende Ausnehmung ausgebildet, die korrespondierend zum axialen Ende des Zylinders 82 ausgeformt ist.At this end of the second Axialkolbenteils another annular recess extending in the axial direction is formed, which is formed corresponding to the axial end of the cylinder 82.

In der dargestellten Position des Ankers 22 liegt keine Bestromung der Spule 14 vor. Erfindungsgemäß ist der Einlass 26 über die Durchgangsbohrung 40, den Spalt 67, den Kolbenraum 72, die Öffnungen 80, 106 der Einlegeteile 68, 100 sowie den Auslassraum 104 mit dem Auslass 30 fluidisch verbunden. Dies wird dadurch erreicht, dass die zweite Druckfeder 108 den zweiten Axialkolbenteil 64 in Richtung des ersten Axialkolbenteils 38 drückt und die erste Druckfeder den ersten Axialkolbenteil 38 mit dem Anker 22 in Richtung des Einlasses 26 drückt, so dass der Spalt 67 zwischen den beiden Axialkolbenteilen 38, 64 entsteht, der in den anderen Stellungen des Ankers 22 beziehungsweise in den anderen Bestromungszuständen der Spule 14 verschlossen ist. Wird eine solche Pumpe zur Verstellung eines Verstellringes einer Kühlmittelpumpe verwendet, kann sich also der Druck aus dem Raum zur Verstellung des Rings bei Abschalten oder Ausfall der Bestromung der Pumpe abbauen, so dass eine Maximalförderung der Kühlmittelpumpe durch Rückstellung des Verstellringes sichergestellt wird.In the illustrated position of the armature 22, there is no energization of the coil 14. According to the invention, the inlet 26 is fluidically connected to the outlet 30 via the through-bore 40, the gap 67, the piston space 72, the openings 80, 106 of the inserts 68, 100 and the outlet space 104. This is achieved in that the second compression spring 108 presses the second Axialkolbenteil 64 in the direction of the first Axialkolbenteils 38 and the first compression spring presses the first Axialkolbenteil 38 with the armature 22 in the direction of the inlet 26, so that the gap 67 between the two Axialkolbenteilen 38th , 64 is formed, which is closed in the other positions of the armature 22 and in the other Bestromungszuständen the coil 14. If such a pump is used for adjusting an adjusting ring of a coolant pump, then the pressure from the space for adjusting the ring when switching off or failure of the energization of the pump can degrade, so that a maximum promotion of the coolant pump is ensured by provision of the adjusting ring.

Im Betrieb wird der Elektromagnet der Magnetpumpe zwischen einer Teilbestromung und einer Vollbestromung der Spule 14 hin- und hergeschaltet.In operation, the solenoid of the magnetic pump between a Teilbestromung and a full energization of the coil 14 is switched back and forth.

Die Höhe und die Dauer der Teilbestromung wird so gewählt, dass die Kraft der ersten Druckfeder 62 überwunden wird, so dass der erste Axialkolbenteil 38 gegen den zweiten Axialkolbenteil 64 anliegt und somit der Spalt 67 zwischen den beiden Axialkolbenteilen 38, 64 über das Dämpfungselement 66 geschlossen wird, so dass sich die beiden Axialkolbenteile 38, 64 im Betrieb als Einheit bewegen. Die zweite stärkere Druckfeder 108 wird bei Teilbestromung nicht komprimiert, da deren Kraft größer ist als die des Elektromagneten 10 bei Teilbestromung. Der zweite Axialkolbenteil 64 verharrt entsprechend am Anschlag 76. In dieser Position ragt der ringförmige Vorsprung 32 gerade in die ringförmige Ausnehmung 34 im Einlassgehäuse 24, so dass der dazwischen liegende Raum lediglich über Spalte zwischen Anker 22 und Spulenträger 12 beziehungsweise Anker 22 und Einlassgehäuse 24 mit dem übrigen Fluid gefüllten Raum verbunden ist. Dies führt zu einer deutlichen Bewegungsdämpfung bei Bewegung des Ankers 22 in Richtung des Einlasses 26 durch den in diesem Raum nur langsam über die Spalte abzubauenden Druck.The height and duration of the partial energization is selected so that the force of the first compression spring 62 is overcome, so that the first Axialkolbenteil 38 abuts against the second Axialkolbenteil 64 and thus the gap 67 between the two Axialkolbenteilen 38, 64 closed via the damping element 66 is, so that the two Axialkolbenteile 38, 64 move in operation as a unit. The second stronger compression spring 108 is not compressed at Teilbestromung because their force is greater than that of the electromagnet 10 at Teilbestromung. In this position, the annular projection 32 protrudes straight into the annular recess 34 in the inlet housing 24, so that the space between them only via gaps between the armature 22 and bobbin 12 or armature 22 and inlet housing 24 with connected to the remaining fluid-filled space. This leads to a significant damping of movement during movement of the armature 22 in the direction of the inlet 26 through the pressure to be degraded in this space only slowly over the gaps.

Wird im Folgenden auf Vollbestromung umgestellt, ist die auf den Anker 22 in Richtung des Auslasses 30 wirkende Kraft größer als die Summe der entgegenwirkenden Kräfte, also der Federkräfte der Federn 62, 108 und der gegebenenfalls vorhandenen an den Bauteilen wirkenden hydraulischen Kräften. Entsprechend wird der Axialkolben 38, 64 als Einheit in Richtung des Auslasses 30 bewegt. Mit dem Axialkolben 38, 64 wird das erste Rückschlagventil 86 im Zylinder 82 Richtung Auslass 30 bewegt, so dass sich im Zylinder 82 ein Druck aufbaut, der schließlich dazu führt, dass das zweite Rückschlagventil 96 gegen seine Federkraft öffnet und Fluid aus dem Zylinder 82 in den Auslassraum 104 strömt. Ein Teil des Fluids verlässt den Auslassraum 104 durch den Auslass 30, während ein anderer Teil des Fluids durch die Öffnungen 80, 106 in den Zwischenraum 74 und den Kolbenraum 72 strömt, da sich das Fluidvolumen im Kolbenraum 72 beim Ausfahren des Kolbenteils 38 nur um einen Bruchteil des ausgestoßenen Fluidvolumens reduziert.If in the following switched to full current, the force acting on the armature 22 in the direction of the outlet 30 is greater than the sum of the counteracting forces, ie the spring forces of the springs 62, 108 and the possibly existing acting on the components hydraulic forces. Accordingly, the axial piston 38, 64 is moved as a unit in the direction of the outlet 30. With the axial piston 38, 64, the first check valve 86 is moved in the cylinder 82 toward the outlet 30, so that in the cylinder 82, a pressure builds up, which eventually causes the second check valve 96 opens against its spring force and fluid from the cylinder 82 in the outlet space 104 flows. A portion of the fluid exits the outlet space 104 through the outlet 30, while another portion of the fluid passes through the openings 80, 106 in the Gap 74 and the piston chamber 72 flows, since the fluid volume in the piston chamber 72 when extending the piston member 38 is reduced only by a fraction of the expelled fluid volume.

Wird im Folgenden die Bestromung wieder auf Teilbestromung gestellt, bewegt sich der Axialkolben 38, 64 als Einheit in Richtung des Einlasses 26. Aufgrund seiner Trägheit und des bei dieser Bewegung im durch das zweite Rückschlagventil 96 nunmehr geschlossenen Zylinder 82 entstehenden Unterdrucks folgt das erste Rückschlagventil 86 dem Axialkolben 38, 64 deutlich verzögert, da seine Federkraft für eine bleibende Anlage am Axialkolben 38, 64 nicht ausreicht. Bei dieser Bewegung wird durch diesen Unterdruck auch Fluid durch die axiale Durchgangsbohrung 40, 83 in den Zylinder 82 gesaugt, strömt also durch den Spalt zwischen dem ersten Rückschlagventil 86 und dem Axialkolben 38, 64 hindurch in den Zylinder 82. Im Kolbenraum 72 wird durch diese Bewegung ein Überdruck erzeugt, der dazu führt, dass das Fluid aus dem Kolbenraum 72 durch die Öffnungen 80, 106 und die Räume 74, 104 zum Auslass 30 gedrückt wird, so dass eine weitere Förderung stattfindet. Durch den folgenden Druckausgleich legt sich das erste Rückschlagventil 86 wieder gegen den Axialkolben 38, 64 an, so dass die Anfangsstellung wieder erreicht ist. Die Kraft für diese Bewegung liefert die Druckfeder 108. Dieser Vorgang wird beliebig häufig je nach gefordertem Volumenstrom wiederholt.If in the following the energization is again set to partial energization, the axial piston 38, 64 moves as a unit in the direction of the inlet 26. Due to its inertia and the resulting in this movement in the now closed by the second check valve 96 cylinder 82 negative pressure follows the first check valve 86th the axial piston 38, 64 significantly delayed because its spring force for a permanent contact with the axial piston 38, 64 is not sufficient. During this movement, fluid is also sucked through the axial passage bore 40, 83 into the cylinder 82, thus flowing through the gap between the first check valve 86 and the axial piston 38, 64 into the cylinder 82. In the piston chamber 72 is through this Movement generates an overpressure, which causes the fluid from the piston chamber 72 through the openings 80, 106 and the spaces 74, 104 is pressed to the outlet 30, so that a further promotion takes place. Due to the following pressure equalization, the first check valve 86 again bears against the axial piston 38, 64, so that the initial position is reached again. The force for this movement is provided by the compression spring 108. This process is repeated as often as required, depending on the required volume flow.

Durch Aufhebung der Bestromung werden die beiden Axialkolbenteile 38, 64 wieder getrennt, da die Druckfeder 108 den zweiten Axialkolbenteil 64 gegen den Anschlag 76 drückt und die Druckfeder 62 den ersten Axialkolbenteil 38 vom zweiten Axialkolbenteil 64 wegdrückt. Entsprechend besteht der bereits beschriebene freie Strömungsweg zwischen dem Einlass 26 und dem Auslass 30.By canceling the energization, the two Axialkolbenteile 38, 64 are separated again, since the compression spring 108 presses the second Axialkolbenteil 64 against the stop 76 and the compression spring 62 pushes the first Axialkolbenteil 38 from the second Axialkolbenteil 64. Accordingly, the already described free flow path exists between the inlet 26 and the outlet 30.

Alle stattfindenden Bewegungen aufgrund einer Bestromungsänderung werden jeweils gedämpft. Einerseits besteht eine Dämpfung der Anschläge zwischen dem Anker 22 und dem Kern 20, dem ersten Axialkolbenteil 38 und dem zweiten Axialkolbenteil 64 sowie dem zweiten Axialkolbenteil 64 und dem Anschlag 76 aufgrund der elastischen Dämpfungselemente 48, 66, 78 andererseits durch der hydraulischen Dämpfungskammer zwischen dem Einlassgehäuse 24 und dem Anker 22 aufgrund des zur Ausnehmung 34 korrespondierenden Vorsprungs 32.All occurring movements due to a current change are attenuated. On the one hand there is a damping of the stops between the armature 22 and the core 20, the first Axialkolbenteil 38 and the second Axialkolbenteil 64 and the second Axialkolbenteil 64 and the stop 76 due to the elastic damping elements 48, 66, 78 on the other hand by the hydraulic damping chamber between the inlet housing 24 and the armature 22 due to the recess 34 corresponding projection 32nd

Eine weitere hydraulische Dämpfungskammer wird bei der Bewegung des zweiten Axialkolbenteils 64 in Richtung des Auslasses 30 wirksam. Die radiale Erweiterungsfläche 75 des zweiten Axialkolbenteils 64 ist an ihrem Außenumfang in Richtung des Zylinders 82 gebogen und zwar derart, dass zwischen dem hohlzylinderförmigen Teil, welches in den Zylinder gefahren werden kann und dieser Fläche eine ringförmige Ausnehmung 110 entsteht. In diese greift das zum Einlass 26 weisende Ende des Zylinders 82 bei der Bewegung des Axialkolbens 38, 64 in Richtung des Auslasses 30, so dass das in der Ausnehmung 110 vorhandene Fluid lediglich über Spalte entweichen kann und so die Bewegung dämpft.Another hydraulic damping chamber becomes effective in the movement of the second Axialkolbenteils 64 in the direction of the outlet 30. The radial extension surface 75 of the second Axialkolbenteils 64 is bent at its outer periphery in the direction of the cylinder 82 in such a way that between the hollow cylindrical part, which can be driven into the cylinder and this surface an annular recess 110 is formed. In this engages the inlet 26 facing the end of the cylinder 82 during the movement of the axial piston 38, 64 in the direction of the outlet 30, so that the existing fluid in the recess 110 can escape only through gaps and thus dampens the movement.

Zusätzlich wird durch die Querbohrung 42 im ersten Axialkolbenteil 38 sowie die Bohrung 46 im Kern 20 ein unerwünschter Dämpfungseffekt der Ankerbewegung durch Kompression oder Unterdruckbildung im Raum 44 verhindert.In addition, an undesirable damping effect of the armature movement by compression or negative pressure formation in the space 44 is prevented by the transverse bore 42 in the first Axialkolbenteil 38 and the bore 46 in the core 20.

Die erfindungsgemäße Magnetpumpe weist einen sehr geringen Verschleiß auf und bietet einen einfachen und schnellen Druckausgleich zwischen Einlass und Auslass. Gleichzeitig kann bei entsprechender Verwendung der Magnetpumpe diese Funktion der Rückstellung des Ankers auch als fail-safe Funktion genutzt werden. Somit kann auf ein separates Ventil verzichtet werden.The magnetic pump according to the invention has a very low wear and provides a simple and quick pressure equalization between inlet and outlet. At the same time, with appropriate use of the magnetic pump, this function of the provision of the Ankers can also be used as a fail-safe function. Thus it can be dispensed with a separate valve.

Es sollte deutlich sein, dass der Schutzbereich des Hauptanspruchs nicht auf das beschriebene Ausführungsbeispiel beschränkt ist. Auch ist der Schutzbereich des vorliegenden Verfahrensanspruchs nicht auf den Gegenstand des Vorrichtungsanspruchs beschränkt, da eine andere konstruktive Ausgestaltung zur Verwirklichung eines die fluidische Verbindung herstellenden Spaltes ebenfalls denkbar ist.It should be clear that the scope of the main claim is not limited to the embodiment described. Also, the scope of the present method claim is not limited to the subject matter of the device claim, as another structural design for the realization of the fluidic connection producing gap is also conceivable.

Claims (17)

  1. A magnet pump for an auxiliary assembly of a vehicle, comprising
    an inlet (26) and an outlet (30),
    an electromagnet (10) comprising a translatorily movable armature (22), a core (20), a coil (14) and a yoke (16),
    an axial piston (38, 64) adapted to be moved up and down in a cylinder (82),
    a first non-return valve (86) biased against said axial piston (38, 64),
    a second non-return valve (96) biased against an outlet opening (92) of said cylinder (82),
    characterized in that
    said axial piston (38, 64) is of bipartite configuration and comprises an axial through bore (40, 83), wherein said first axial piston part (38) is connected with said armature (22) or is integrally formed with said armature (22) and is adapted to be lifted off said second axial piston part (64), wherein, when the coil is not energized, in the lifted-off state a fluidic connection exists between said inlet (26) and said outlet (30) via a gap (67) between said two axial piston parts (38, 64).
  2. The magnet pump for an auxiliary assembly of a vehicle according to claim 1,
    characterized in that
    between the first axial piston part (38) and the second axial piston part (64) a compression spring (62) is arranged.
  3. The magnet pump for an auxiliary assembly of a vehicle according to any one of claims 1 or 2,
    characterized in that
    the second axial piston part (64) rests upon a stopper (76) due to the compression force of a second compression spring (108), which is stronger as compared with the first compression spring (62), when the armature (22) is completely reset, and rests upon the first axial piston part (38) in the operating positions of the armature (22) during pump operation.
  4. The magnet pump for an auxiliary assembly of a vehicle according to claim 3,
    characterized in that
    the stopper (76) is defined at a first insert housing part (68).
  5. The magnet pump for an auxiliary assembly of a vehicle according to any one of the preceding claims,
    characterized in that
    the first non-return valve (86) is biased against the second axial piston part (64) via a first spring (88) and the second non-return valve (96) is biased against the outlet opening (92) of the cylinder (82) via a second spring (98).
  6. The magnet pump for an auxiliary assembly of a vehicle according to any one of the preceding claims,
    characterized in that
    the first axial piston part (38) is connected with the armature (22) via a bore (36) in said armature (22).
  7. The magnet pump for an auxiliary assembly of a vehicle according to any one of the preceding claims,
    characterized in that
    the effective diameter of the second axial piston part (64) is larger than the effective diameter of the first axial piston part (38).
  8. The magnet pump for an auxiliary assembly of a vehicle according to any one of the preceding claims,
    characterized in that
    the inlet (26) and the outlet (30) are arranged at axially opposite ends of the magnet pump, wherein the armature (22) is arranged at the side of the inlet (26) and the non-return valves (86, 96) and the second axial piston part (64) are arranged at the side of said outlet (30).
  9. The magnet pump for an auxiliary assembly of a vehicle according to any one of the preceding claims,
    characterized in that
    in an outlet housing (28) where the outlet (30) is defined a second insert housing part (100) is arranged in which the cylinder (82) is defined in which the second axial piston part (64) is guided and the second non-return valve (86) is arranged, wherein the second non-return valve (96) is loaded against the outlet opening (92) of said cylinder (82) which leads into an outlet space (104) that ends in said outlet (30).
  10. The magnet pump for an auxiliary assembly of a vehicle according to claim 9,
    characterized in that
    a continuous fluidic connection exists between a piston space (72) into which the first axial piston part (38) extends and an intermediate space (74) surrounding the cylinder (82) and the outlet space (104).
  11. The magnet pump for an auxiliary assembly of a vehicle according to claim 10,
    characterized in that
    the fluidic connection is established via openings (80, 106) in the second insert housing part (100) and in the first insert housing part (68) where the stopper (76) arranged between the intermediate space (74) and the piston space (72) is defined.
  12. The magnet pump for an auxiliary assembly of a vehicle according to any one of the preceding claims,
    characterized in that
    the spring (88) of the first non-return valve (86) is configured such that said first non-return valve (86) delayedly follows the second axial piston part (64) during its movement towards the inlet (26).
  13. The magnet pump for an auxiliary assembly of a vehicle according to any one of the preceding claims,
    characterized in that
    in the first axial piston part (38) and at the core (20) a respective transverse bore (42, 46) is defined in the inlet-side area.
  14. The magnet pump for an auxiliary assembly of a vehicle according to any one of the preceding claims,
    characterized in that
    at the second axial piston part (64) in the area of the stopper (76) and/or in the area of resting upon the first axial piston part (38) and/or between the armature (22) and the core (20) elastic damping elements (48, 66, 78) are arranged.
  15. The magnet pump for an auxiliary assembly of a vehicle according to any one of claims 9 to 14,
    characterized in that
    at the second axial piston part (64) an annular recess (110) facing the second insert housing part (100) is defined into which an axial end of the cylinder (82) is inserted when the armature (22) is fully adjusted towards the outlet (30).
  16. The magnet pump for an auxiliary assembly of a vehicle according to any one of the preceding claims,
    characterized in that
    at the side of the inlet (26) an annular recess (34) is defined at an inlet housing (24) of the magnet pump into which a corresponding annular projection (32) of the armature (22) facing said inlet (26) is inserted when said armature (22) is fully reset.
  17. A method for controlling a magnet pump for an auxiliary assembly of a vehicle, wherein
    an axial piston (38, 64) coupled with an armature (22) of an electromagnet (10) is moved up and down in a cylinder (82) due to an alternate current feed to a coil (14) of said electromagnet (10) for the purpose of delivering a fluid from an inlet (26) to an outlet (30),
    characterized in that
    said axial piston (38, 64) is of bipartite configuration and comprises an axial through bore (40, 83), wherein said first axial piston part (38) is connected with said armature (22) or is integrally formed with said armature (22) and is adapted to be lifted off said second axial piston part (64), wherein, when the coil is not energized, said armature (22) is pressed into its fully retracted position in which a gap (67) is continuously cleared in this position of said armature (22) by said first axial piston part (38) connected or integrally formed with said armature (22), via which gap a fluidic connection between said inlet (26) and said outlet (30) is established.
EP14755616.1A 2013-11-08 2014-08-12 Magnetic pump for an uxiliary assembly of a vehicle and method of controlling a magnetic pump for an auxiliary assembly Active EP3066343B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE201310112306 DE102013112306A1 (en) 2013-11-08 2013-11-08 Magnetic pump for an auxiliary unit of a vehicle and method for controlling a magnetic pump for an auxiliary unit
PCT/EP2014/067247 WO2015067384A1 (en) 2013-11-08 2014-08-12 Magnet pump for an auxiliary assembly of a vehicle, and method for controlling a magnet pump for an auxiliary assembly

Publications (2)

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EP3066343A1 EP3066343A1 (en) 2016-09-14
EP3066343B1 true EP3066343B1 (en) 2017-11-29

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US (1) US10151307B2 (en)
EP (1) EP3066343B1 (en)
DE (1) DE102013112306A1 (en)
WO (1) WO2015067384A1 (en)

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JP1546565S (en) * 2015-08-19 2016-03-28
CN105508698A (en) * 2016-01-15 2016-04-20 徐園植 Self-flow oil pumping energy-saving pump electromagnetic equipment
CN105587441A (en) * 2016-02-15 2016-05-18 徐毓艺 High-efficiency energy-saving environmentally-friendly fuel oil supply pump
DE102020201813A1 (en) 2020-02-13 2021-08-19 Magna Pt B.V. & Co. Kg Oscillating piston pump arrangement and method for operating an oscillating piston pump arrangement
CN112523986A (en) * 2020-11-09 2021-03-19 广西玉柴机器股份有限公司 Water pumping device of vehicle cooling system

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EP3066343A1 (en) 2016-09-14
US10151307B2 (en) 2018-12-11
US20160281695A1 (en) 2016-09-29
WO2015067384A1 (en) 2015-05-14

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