WO2016180579A1 - Pompe magnétique destinée à un groupe auxiliaire d'un véhicule - Google Patents

Pompe magnétique destinée à un groupe auxiliaire d'un véhicule Download PDF

Info

Publication number
WO2016180579A1
WO2016180579A1 PCT/EP2016/057521 EP2016057521W WO2016180579A1 WO 2016180579 A1 WO2016180579 A1 WO 2016180579A1 EP 2016057521 W EP2016057521 W EP 2016057521W WO 2016180579 A1 WO2016180579 A1 WO 2016180579A1
Authority
WO
WIPO (PCT)
Prior art keywords
axial piston
armature
magnetic pump
auxiliary unit
vehicle according
Prior art date
Application number
PCT/EP2016/057521
Other languages
German (de)
English (en)
Inventor
Michael Sanders
Andres Tönnesmann
Original Assignee
Pierburg Gmbh
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Pierburg Gmbh filed Critical Pierburg Gmbh
Priority to EP16714893.1A priority Critical patent/EP3295026A1/fr
Publication of WO2016180579A1 publication Critical patent/WO2016180579A1/fr

Links

Classifications

    • 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
    • F04B17/046—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors using solenoids the fluid flowing through the moving part of the motor

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.
  • 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.
  • 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 rests against an outlet of the cylinder.
  • Such an electric fluid pump is known, for example, from EP 0 288 216 A1.
  • EP 0 288 216 A1 Such an electric fluid pump is known, for example, from EP 0 288 216 A1.
  • 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.
  • the axial piston has an axial bore and is integrally formed and the magnetic pump has a first sealing element on the axial piston, which abuts in each position of the armature against a corresponding first sealing surface on the inner circumference of the cylinder and having a second sealing element, of a corresponding second sealing surface is lifted in a remindströmposition, wherein in the sudströmposition via a gap between the second sealing element and the second sealing surface is a fluidic connection between the inlet and the outlet, a flow through the pump and in particular a return flow from a to be filled by the pump pressure pressure space is possible without using an additionally actuated valve to have to.
  • a sudströmposition is created, for example, for the application of a controlled via a slider coolant pump. This is made possible in that when not energized the coil, the armature or the axial piston is moved to a position in which the flow-through gap is released.
  • the magnetic pump has a first compression spring, via which the axial piston is loaded in the direction of a first operating position, wherein the movement of the axial piston caused by the spring force of the first compression spring is limited by a stop. Accordingly, the two end positions of the pump are set during operation, whereby the sensitivity of the magnetic pump with slightly fluctuating voltages does not affect the approached end positions of the axial piston.
  • the magnetic pump has a second compression spring, which has a lower spring strength than the first compression spring, and over which the second sealing element is loaded in the opening direction.
  • This second spring thus provides either directly or indirectly via interconnected components that in a non-energized state of the electromagnet, the second sealing element is lifted from the sealing surface, whereby a return flow position can be approached in a simple manner.
  • the second sealing element are formed on the outer circumference of the axial piston and the second sealing surface on the inner circumference of the cylinder.
  • this embodiment can be dispensed with additional components, so that the assembly and manufacture can be done inexpensively.
  • the second sealing element is advantageously arranged in the sudströmposition axially outside the sealing surface and the gap is released between the cylinder and the axial piston. Of the necessary gap for connecting the inlet to the outlet is released accordingly by simple adjustment of the axial piston.
  • the two sealing surfaces are formed on the inner circumference of the cylinder, which is stepped, has a transverse bore and is surrounded by an outer housing which is radially spaced from the cylinder in a first portion which extends from the outlet to the transverse bore and hereinafter, closer to the inlet disposed portion sealingly surrounds the cylinder, wherein the second sealing surface is disposed radially within the second axial portion.
  • a flow can take place between the outer housing and the cylinder accommodating the axial piston and subsequently via the transverse bore and the released gap and the transverse bores of the axial piston in the direction of the inlet or in the opposite direction of flow.
  • the first compression spring is clamped between a bearing surface and an axially deformable, resilient element, which is tensioned in both operating end positions in the direction of a stop and bears against a shoulder of the axial piston and rests in the remindströmposition against one of the stops and axially from the axial piston is spaced. Accordingly, the stronger, first compression spring acts only on the ring on the axial piston, which is pressed in the absence of energization of the coil only by the weaker designed second compression spring in the sudströmposition.
  • the control for energizing between the two operating end positions is significantly simplified.
  • the second sealing element is formed by a valve member which corresponds to a valve seat designed as a sealing surface which is formed at one axial end of a bore in a flow housing. Accordingly, the flow paths can be placed in the scrubströmposition outside the magnetic circuit and are thus freely selectable.
  • valve member is arranged in the vomströmposition axially spaced from the valve seat and the gap is released between the valve member and the valve seat and along the bore in the flow housing. Accordingly, the size of the gap can be largely freely chosen.
  • the second compression spring loads the armature in the return flow position against the valve member via an actuating member, which is arranged at least in sections in the bore in the flow housing.
  • the return flow position of the second valve member is thus not dependent on the position of the axial piston, but only on the position of the armature, so that smaller spring forces of the second compression spring are necessary.
  • the armature is mounted in the flow housing and axially displaceable on the axial piston, wherein on the axial piston a shoulder is formed, against which the armature rests in the operating positions.
  • the movement of the armature is transmitted due to the flow of current in the coil via the shoulder on the axial piston, on the one hand in the cylinder and on the other hand via an opening in the armature penetrates through the axial piston adjacent to the shoulder, and is thus mounted on the armature.
  • the axial piston is in this advantageous embodiment in the remindströmposition against a stop on the flow housing or on the core. This facilitates assembly, since no additional stops must be mounted and prevents unwanted displacement of the axial piston when approaching the remindströmposition.
  • the cylinder is arranged in the flow housing radially inside the core of the electromagnet.
  • the outlet is arranged at the armature axial end opposite to the flow housing and radially inside the core, which again reduces the axial space and simplifies installation.
  • the pump pressure is still generated by the magnetic forces.
  • the fluidic connection between the outlet and the inlet is released in the sudströmposition over a space in which the armature is slidably disposed, wherein the axial piston transverse bores and the armature through holes and the actuator are formed.
  • a resilient element is arranged, which is arranged axially between the armature and a ring and in the operating position, in which the armature and the ring abut the core is compressed.
  • FIG. 1 shows a side view of a first embodiment of a magnetic pump according to the invention in a sectional view.
  • FIG. 2 shows a side view of a second embodiment of a magnetic pump according to the invention in a sectional view.
  • FIG 3 shows a side view of a third embodiment of a magnetic pump according to the invention in a sectional view.
  • the magnetic pump shown in Figure 1 has an electromagnet 10.1, which is composed of a wound on a coil support 12.1 coil 14.1, a yoke 16.1, and a core 18.1 and a movable armature 20.1.
  • an electromagnet 10.1 which is composed of a wound on a coil support 12.1 coil 14.1, a yoke 16.1, and a core 18.1 and a movable armature 20.1.
  • the armature 20.1 is pulled by the occurring magnetic forces in a known manner in the direction of the core 18.1.
  • the magnetic pump has an inlet housing 22.1, in which an inlet 24.1 for a fluid is formed, and a flow housing 26.1, in which an outlet 28.1 is formed for the fluid and which is arranged on the side opposite to the inlet housing 22.1 side of the electromagnet 10.1.
  • the armature 20.1 arranged between the core 18.1 and the inlet housing 22.1 has at its axial end facing the flow housing 26.1 a cone 30.1 which, when the coil 14.1 is fully energized, projects into a correspondingly shaped recess 32.1 of the core 18.1.
  • the armature 20.1 has a central axial through-bore 34.1, which opens into an axial bore 36.1 of an axial piston 38.1, at whose end facing the flow housing 26.1 a valve seat 40.1 of a first check valve 42.1 is arranged, the valve body 44.1 by means of a spring 46.1 against the valve seat 40.1 is loaded.
  • a second check valve 48.1 is arranged in the flow housing 26.1 in the region of the outlet 28.1 and likewise has a valve body 54.1 prestressed against a valve seat 50.1 by means of a spring 52.1, by means of which an outlet opening 55.1 is closed.
  • the axial piston 38.1 is slidably guided in a cylinder 56.1, which is formed on the inner circumference of the flow housing 26.1.
  • the axial piston 38.1 has an extension of its outer circumference formed in the region of the first check valve 42.1, which serves as a first sealing element 58.1, which cooperates with a sealing surface 60.1 formed by the inner circumference of the cylinder 56.1 bearing against the sealing element 58.1.
  • the axial piston 38.1 has a further radial extension serving as the second sealing element 62.1, which likewise corresponds to the inner circumference of the cylinder 56.1 serving as the second sealing surface 64.1. Between the two serving as a sealing surface 60.1, 64.1 sections of the cylinder 56.1, this has a transverse bore 66.1.
  • the flow housing 26.1 is surrounded radially by an outer housing 68.1, which in a first axial section between the outlet 28.1 and the transverse bore 66.1 radial to Flow housing 26.1 is spaced and in the axially adjacent, closer to the electromagnet 10.1 located axial portion of the flow housing 26.1 sealingly surrounds.
  • the axial piston 38.1 is surrounded by two compression springs 70.1, 72.1, of which a first, stronger compression spring 70.1 is axially clamped between a radially extending bearing surface 74.1 of the flow housing 26.1 and an axially resilient element 76.1 in the form of an axially elastically deformable ring whose opposite axial end in the illustrated position abuts against a shoulder 78.1 of the axial piston 38.1.
  • the second, weaker compression spring 72.1 surrounds the axial piston 38.1 directly and also abuts with its first axial end against a solid support surface 80.1 and with its opposite axial end against a further shoulder 82.1 of the axial piston 38.1.
  • the coil 14.1 is partially energized.
  • This means that the armature 20.1 is pulled by the force of the electromagnet 10.1 in the direction of the core 18.1, with one having a magnetic force which is greater than the spring force of the second piston acting on the axial piston 38.1 and thus on the armature 20.1 Compression spring 72.1, but smaller than the spring force of the force acting on the axial piston 38.1 first compression spring 70.1.
  • the first compression spring pushes the resilient element 76.1, which is slightly deformed in this position, against a stop 84.1, which is formed on an annular projection 85.1 of the core 18.1.
  • the force of the electromagnet 10.1 ensures in this position that the armature 20.1 pushes the axial piston 38.1 from the other side against the resilient element 76.1.
  • the interior 86.1 is reduced by this movement, so that the fluid present in the interior is compressed until the force acting on the valve body 54.1 by the force is greater than the force of the spring 52.1 of the second check valve 48.1, so that this opens, the outlet opening 55.1 is released and the fluid is conveyed through the outlet 28.1.
  • a fluid flow is prevented by the first sealing element 58.1.
  • the resilient element 76.1 In the second operating position of the magnetic pump reached at the end of this movement, the resilient element 76.1, with its opposite axial end, is compressed against a second stop 88.1 formed on the flow housing 26.1. If, in the following, switching back to partial energization of the coil 14. 1, the armature 20. 1 and with it also the axial piston 38. 1 again moves away from the core 18. 1 due to the spring forces. As a result of this movement, a negative pressure is created in the interior 86.1, which ensures that the second check valve 48.1 again closes the outlet opening 55.1 and, on the other hand, lifts the valve body 44.1 of the first check valve 42.1 from its valve seat 40.1, counter to the spring force of the spring 46.1.
  • the invention provides that the magnetic pump has a return flow position in which a steady fluidic Connection between the inlet 24.1 and the outlet 28.1 is. If the energization of the coil 14.1 is completely interrupted, the second compression spring 72.1 presses the axial piston 38.1 and with it the armature 20.1 in the direction of the inlet 24.1. In this case, the axial piston 38.1 rises from the resilient element 76.1 and the second sealing element 62.1 is axially displaced so far that it is arranged outside the sealing surface 64.1 of the cylinder 56.1.
  • FIG. 2 differs from that of FIG. 1 in that the direction of action of the electromagnet 10.2 has been reversed, which means that the ejection movement of the pump takes place when partial energization of the electromagnet 10.2 and the suction movement at full energization. Accordingly, the armature 20.2 surrounds the axial piston 38.2 and the core 18.2 is located between the inlet 24.2 and the armature 20.2, which is guided in the flow housing 26.2.
  • the coil 14.2 is partially energized.
  • the electromagnetic force is greater than the spring force of the second compression spring 72.2, which is located within the pot-shaped armature 20.2 and is clamped between a bottom surface 96.2 of the armature 20.2 and a shoulder 82.2 of the axial piston 38.2.
  • the first compression spring 70.2 is located within a central passage opening 98.2 of the core 18.2 and is biased between the inlet housing 22.2 and the axial end of the axial piston 38.2 clamped, which extends into the core 18.2 and in this position by the first compression spring 70.2 against a stop 100.2 is pressed on the core 18.2, so that this first operating position is taken again as soon as the electromagnetic force between the spring force of the first compression spring 70.2 and the spring force of the second compression spring is 72.2.
  • the armature 20.2 is accelerated in the direction of the core 18.2.
  • the armature 20.2 bears against a shoulder 102.2 on the axial piston 38.2, so that over this shoulder 102.2 and the axial piston 38.2 is moved against the force of the first compression spring 70.2 in the interior of the core 18.2.
  • a lower pressure arises, through which the first check valve 42.2 opens, so that fluid is drawn into the inner space 86.2 from the inlet 24.2 via the axial bore 36.2 of the axial piston until an equilibrium of forces exists on the valve body 44.2 and the check valve 42.2 closes again.
  • a ring 104.2 arranged in the armature 20.2 reaches a stop 84.2, which is formed on an annular projection 85.2 of the core 18.2.
  • the ring 104.2 is pressed by an axially resilient element 76.2 against a stop 106.2 on the inside of the armature 20.2 and lifted by the abutment of the ring on the stop 84.2 of this stop 106.2 on the armature 20.2 under compression of the resilient member 76.2.
  • the armature is 20.2 moved by the force of the second compression spring 72.2 on the axial piston 38.2 in the direction of the outlet 28.2.
  • the armature 20.2 reaches an actuating member 110.2, which is located in a bore 112.2 of FIG
  • Flow housing 26.2 is arranged, via which the outlet 28.2 is fluidically connected to a space 114.2, in which the armature slides 20.2, so that via the bore 112.2 both check valves 42.2,
  • the actuator 110.2 in the form of a valve rod is integrally connected to a valve member 116.2 which acts as a second sealing element 62.2 and which corresponds to a valve seat 118.2 acting as a second sealing surface 64.2.
  • the valve member 116.2 is pressed by a spring element 120.2 in its closed position, and only opens when the armature presses 20.2 through the second compression spring 72.2 from the opposite side against the actuator 110.2.
  • the third exemplary embodiment described below according to FIG. 3 differs in that a first part of the flow housing 26.3, in which the outlet 28.3, the cylinder 56.3 and the two non-return valves 42.3,
  • a filter element 123.3 is integrated into the flow housing 26.3, which filters out impurities in front of the inlet into the pump.
  • An inlet port 124.3 is disposed on the same axial side of the solenoid 10.3 as an outlet port 126.3 connected to the outlet 28.3 and the outlet port 55.3, respectively.
  • An inlet channel 128.3 connected to the inlet port 124.3 extends radially outward of the electromagnet 10.3 to the axially opposite side, to which a second part of the flow housing 26.3 is fixed, in which the inlet channel 128.3 extends radially to the central axis of the magnetic pump, from where the inlet channel 128.3 extends axially into the space 114.3, in which the armature 20.3 is arranged axially movable.
  • This inlet 24.3 is radially bounded by an annular, axially extending projection 132.3.
  • the annular projection 132.3 is thus arranged axially opposite to the axial piston 38.3 and serves as a stop 134.3 for limiting its axial movement.
  • a second outlet channel 136.3 At the radially opposite to the axially extending inlet channel 128.3 side of the electromagnet 10.3 is a second outlet channel 136.3, which is not visible in the figure connected to the outlet 28.3.
  • This outlet channel 136.3 also extends radially in the second part of the flow housing 26.3 in the direction of the armature 20.3. It opens on a valve seat 118.3, which acts as a second sealing surface 64.3, onto which a spherical valve member 116.3 is pressed via spring element 120.3, which serves as a second sealing element 62.3.
  • This valve member 116.3 can be lifted off the valve seat 118.3 by means of an actuating member 110.3, which is fastened to the armature 20.3 and guided in a bore 112.3.
  • the coil 14.3 is partially energized.
  • the electromagnetic force is greater than the spring force of the second compression spring 72.3, which is arranged according to the second embodiment.
  • the first compression spring 70.3 is located within a central passage opening 98.3 of the core 18.3 and is biased between the cylinder 56.3 forming part of the flow housing 26.3 and a radially extending annular projection 138.3 of the axial piston 38.3 clamped on the opposite support surface, the second compression spring 72.3 rests.
  • the axial piston 38.3 is pressed by the first compression spring 70.3 against serving as a stop 134.3 annular projection 132.3, so that this first operating position is taken again as soon as the electromagnetic force between the spring force of the first compression spring 70.3 and the spring force of the second compression spring 72.3.
  • the armature 20.3 is accelerated in the direction of the core 18.3.
  • the armature 20.3 abuts axially against a shoulder 102.3 on the axial piston 38.3, so that over this shoulder 102.3 and the axial piston 38.3 is displaced against the force of the first compression spring 70.3 in the cylinder 56.3.
  • an overpressure is created by the compression, through which the second check valve 48.3 releases the outlet opening 55.3, so that fluid is conveyed from the interior 86.3 to the outlet 28.3.
  • This movement is again attenuated by the axially resilient element 76.3 in the same way as described for the second embodiment, and stored for the rearward movement energy, by which an accelerated movement of the armature 20.3 is formed when switching to Operabestromung.
  • the armature 20.3 and with it the actuator 110.3 is displaced by the force of the second compression spring 72.3 on the axial piston 38.3 in the direction of the inlet 24.3.
  • the actuator 110.3 reaches the valve member 116.3, so that it is lifted from its valve seat 118.3.
  • the magnetic pumps according to the invention have a very low wear and provide a simple and quick pressure equalization between the inlet and outlet in case of failure or switching off the electromagnet.
  • this function of resetting the armature in its vomströmposition can also be used as a fail-safe function with appropriate use of the solenoid.
  • the structure is significantly simplified compared to known designs, so that the assembly is facilitated. Impacts caused by the movement of the axial piston or the armature are significantly dampened and still allows rapid switching with an accelerated armature. simultaneously An undesirable hydraulic back pressure, which would require an increased magnetic force prevented.

Landscapes

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

Abstract

On connaît des pompes magnétiques destinées à des groupes auxiliaires de véhicules, par exemple des pompes de fluide de refroidissement mécaniques à régulation du débit, comportant une entrée (24.1 ; 24.2 ; 24.3) et une sortie (28.1 ; 28.2 ; 28.3), un électroaimant (10.1 ; 10.2 ; 10.3) muni d'un induit (20.1 ; 20.2 ; 20.3) effectuant un mouvement de translation, d'un noyau (18.1 ; 18.2 ; 18.3), d'une bobine (14.1 ; 14.2 ; 14.3) et d'une culasse (16.1 ; 16.2 ; 16.3), un piston axial (38.1 ; 38.2 ; 38.3) effectuant un mouvement alternatif dans un cylindre (56.1 ; 56.2 ; 56.3), une première soupape antiretour (42.1 ; 42.2 ; 42.3) précontrainte par rapport au piston axial (38.1 ; 38.2 ; 38.3), et une deuxième soupape antiretour (48.1 ; 48.2 ; 48.3) précontrainte par rapport à une ouverture de sortie (55.1 ; 55.2 ; 55.3). Des soupapes supplémentaires étaient jusqu'à présent nécessaires pour détendre un espace rempli par la pompe. L'invention vise à ce que cette détente puisse être obtenue même sans soupapes avec des moyens les plus simples possibles. À cet effet, le piston axial (38.1 ; 38.2 ; 38.3) présente un trou axial (36.1 ; 36.2 ; 36.3) et est réalisé d'un seul tenant, et la pompe magnétique présente au niveau du piston axial (38.1 ; 38.2 ; 38.3) un premier élément d'étanchéité (58.1 ; 58.2 ; 58.3) qui, dans chaque position de l'induit (20.1 ; 20.2 ; 20.3), repose contre une première surface d'étanchéité (60.1 ; 60.2 ; 60.3) correspondante au niveau de la circonférence intérieure du cylindre (56.1 ; 56.2 ; 56.3) et présente un deuxième élément d'étanchéité (62.1 ; 62.2 ; 62.3), qui est soulevé d'une deuxième surface d'étanchéité (64.1 ; 64.2 ; 64.3) correspondante dans une position de reflux. Dans la position de reflux, une communication fluidique est créée entre l'entrée (24.1 ; 24.2 ; 24.3) et la sortie (28.1 ; 28.2 ; 28.3) par l'intermédiaire d'un interstice (94.1 ; 94.2 ; 94.3) entre le deuxième élément d'étanchéité (62.1 ; 62.2 ; 62.3) et la deuxième surface d'étanchéité (64.1 ; 64.2 ; 64.3).
PCT/EP2016/057521 2015-05-08 2016-04-06 Pompe magnétique destinée à un groupe auxiliaire d'un véhicule WO2016180579A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP16714893.1A EP3295026A1 (fr) 2015-05-08 2016-04-06 Pompe magnétique destinée à un groupe auxiliaire d'un véhicule

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102015107207.6 2015-05-08
DE102015107207.6A DE102015107207A1 (de) 2015-05-08 2015-05-08 Magnetpumpe für ein Hilfsaggregat eines Fahrzeugs

Publications (1)

Publication Number Publication Date
WO2016180579A1 true WO2016180579A1 (fr) 2016-11-17

Family

ID=55697189

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2016/057521 WO2016180579A1 (fr) 2015-05-08 2016-04-06 Pompe magnétique destinée à un groupe auxiliaire d'un véhicule

Country Status (3)

Country Link
EP (1) EP3295026A1 (fr)
DE (1) DE102015107207A1 (fr)
WO (1) WO2016180579A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2020115776A1 (fr) * 2018-12-03 2020-06-11 Ceme S.P.A. Pompe pour doser un fluide

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
IT201800003069A1 (it) * 2018-02-27 2019-08-27 Elbi Int Spa Pompa a vibrazione con attuazione migliorata
DE102020201813A1 (de) 2020-02-13 2021-08-19 Magna Pt B.V. & Co. Kg Schwingkolbenpumpenanordnung sowie Verfahren zum Betreiben einer Schwingkolbenpumpenanordnung

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0288216A1 (fr) * 1987-04-15 1988-10-26 Eaton S.A.M. Pompe électrique à liquides
DE102005048765A1 (de) * 2005-10-10 2007-04-12 Aweco Appliance Systems Gmbh & Co. Kg Schwingankerpumpe
DE102008013440A1 (de) * 2008-03-10 2009-09-17 Thomas Magnete Gmbh Magnetbetätigte Hubkolbenpumpe mit hydraulischer Dämpfung
WO2011029577A1 (fr) * 2009-09-09 2011-03-17 Rudolf Lonski Pompe à armature oscillante

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1088164B1 (fr) * 1998-05-15 2003-03-19 Rolland Versini Motopompe a ecoulement axial traversant avec debitmetre incorpore et pressostat
JP4186256B2 (ja) * 1998-06-17 2008-11-26 株式会社日本自動車部品総合研究所 電磁弁一体型電磁ポンプ
DE102008010073B4 (de) * 2008-02-19 2010-10-21 Thomas Magnete Gmbh System und Verfahren zum Dosieren eines Fluids
DE202008007146U1 (de) * 2008-05-27 2008-08-14 Lincoln Gmbh Pumpenelement
DE102013112306A1 (de) 2013-11-08 2015-05-13 Pierburg Gmbh Magnetpumpe für ein Hilfsaggregat eines Fahrzeugs sowie Verfahren zur Steuerung einer Magnetpumpe für ein Hilfsaggregat

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0288216A1 (fr) * 1987-04-15 1988-10-26 Eaton S.A.M. Pompe électrique à liquides
DE102005048765A1 (de) * 2005-10-10 2007-04-12 Aweco Appliance Systems Gmbh & Co. Kg Schwingankerpumpe
DE102008013440A1 (de) * 2008-03-10 2009-09-17 Thomas Magnete Gmbh Magnetbetätigte Hubkolbenpumpe mit hydraulischer Dämpfung
WO2011029577A1 (fr) * 2009-09-09 2011-03-17 Rudolf Lonski Pompe à armature oscillante

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2020115776A1 (fr) * 2018-12-03 2020-06-11 Ceme S.P.A. Pompe pour doser un fluide

Also Published As

Publication number Publication date
EP3295026A1 (fr) 2018-03-21
DE102015107207A1 (de) 2016-11-10

Similar Documents

Publication Publication Date Title
EP3066343B1 (fr) Pompe magnétique pour agrégat auxiliaire de véhicule automobile et procédé de contrôle de pompe magnétique pour agrégat auxiliaire
DE102007034038A1 (de) Hochdruckpumpe für ein Kraftstoffsystem einer Brennkraftmaschine
DE102014113566B3 (de) Elektromagnetventil für einen Verbrennungsmotor
DE10051614B4 (de) Elektromagnetisches Ventil
EP3371463B1 (fr) Système de régulation d'une pompe à liquide de refroidissement à régulation mécanique d'un moteur à combustion interne
EP1771675B1 (fr) Soupape a commande electrique
DE112017005629T5 (de) Hochdruckkraftstoffversorgungspumpe mit elektromagnetischem einlassventil
DE102013101038B3 (de) Ventilvorrichtung für einen Hydraulikkreislauf sowie Ölpumpenregelanordnung
WO2016180579A1 (fr) Pompe magnétique destinée à un groupe auxiliaire d'un véhicule
EP2483561B1 (fr) Pompe pour appareil de nettoyage haute pression
DE102012104456B3 (de) Ventilvorrichtung für einen Hydraulikkreislauf sowie Ölpumpenregelanordnung
EP2690327B1 (fr) Distributeur hydraulique
DE102010025171A1 (de) Fluiddruckumschaltventil
DE102009027706A1 (de) Regelventil für ein Fahrzeugbremssystem und korrespondierendes Fahrzeugbremssystem
EP2519732B1 (fr) Vanne de controle du debit de commande electrique, destinee en particulier a commander le debit d'une pompe haute pression a carburant
WO2010072201A1 (fr) Soupape pilote et machine hydraulique à commande par soupape
DE102012004735B4 (de) Hubkolbenpumpe mit elektromagnetischen Antrieb, mit Lagerung des Ankers auf einer Stange und einer Ventilanordnung bestehend aus einer hubabhängigen Schlitzsteuerung
DE102017211361A1 (de) Ventileinrichtung für eine Kraftstoffhochdruckpumpe
EP1573212B1 (fr) Electroaimant
DE102009022974A1 (de) Elektromagnetisch betätigtes Schnellschaltventil als Einlassventil einer hydraulischen Antriebseinheit
DE112018002148T5 (de) Hochdruckkraftstoffversorgungspumpe
WO2010020241A1 (fr) Système de soupapes et hydromachine commandée par soupapes
EP3642516A1 (fr) Vanne proportionnelle servant à réguler un flux de substance gazeuse
DE102010020834A1 (de) Elektromagnetisches Regelventil
DE112018003099T5 (de) Solenoideinlassventil und damit versehene hochdruck-kraftstoffpumpe

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 16714893

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: DE