EP3066343A1 - Magnet pump for an auxiliary assembly of a vehicle, and method for controlling a magnet pump for an auxiliary assembly - Google Patents

Magnet pump for an auxiliary assembly of a vehicle, and method for controlling a magnet pump for an auxiliary assembly

Info

Publication number
EP3066343A1
EP3066343A1 EP14755616.1A EP14755616A EP3066343A1 EP 3066343 A1 EP3066343 A1 EP 3066343A1 EP 14755616 A EP14755616 A EP 14755616A EP 3066343 A1 EP3066343 A1 EP 3066343A1
Authority
EP
European Patent Office
Prior art keywords
armature
axial piston
outlet
inlet
magnetic pump
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP14755616.1A
Other languages
German (de)
French (fr)
Other versions
EP3066343B1 (en
Inventor
Andres Tönnesmann
Matthias Baden
Costantino Brunetti
Michael Sanders
Andreas Köster
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Pierburg GmbH
Original Assignee
Pierburg GmbH
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
Priority to DE201310112306 priority Critical patent/DE102013112306A1/en
Application filed by Pierburg GmbH filed Critical Pierburg GmbH
Priority to PCT/EP2014/067247 priority patent/WO2015067384A1/en
Publication of EP3066343A1 publication Critical patent/EP3066343A1/en
Application granted granted Critical
Publication of EP3066343B1 publication Critical patent/EP3066343B1/en
Application status is Active legal-status Critical
Anticipated expiration legal-status Critical

Links

Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04BPOSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B17/00Pumps characterised by combination with, or adaptation to, specific driving engines or motors
    • F04B17/03Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors
    • F04B17/04Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors using solenoids
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04BPOSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B17/00Pumps characterised by combination with, or adaptation to, specific driving engines or motors
    • F04B17/03Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors
    • F04B17/04Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors using solenoids
    • F04B17/042Pumps 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
    • F04B17/044Pumps 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
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04BPOSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/10Valves; Arrangement of valves
    • F04B53/12Valves; Arrangement of valves arranged in or on pistons
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04BPOSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/14Pistons, piston-rods or piston-rod connections

Abstract

Magnet pumps are known for auxiliary assemblies in vehicles, comprising an inlet (26) and an outlet (30), an electromagnet (10), an axial piston (38, 64) which can be moved up and down in a cylinder (82), a first non-return valve (86) which is pre-tensioned against the axial piston (38, 64), and a second non-return valve (96) which is pre-tensioned against an outlet opening (92) of the cylinder (82). It is also known that an axial piston (38, 64) coupled to an armature (22) of an electromagnet (10) is moved up and down by alternately supplying a current to a coil (14) of the electromagnet (10) in a cylinder (82) for pumping a fluid from the inlet (26) to the outlet (30). Until now, additional valves had to be used in order to depressurize an area filled via the pump. According to the invention, this is prevented in that the axial piston (38, 64) is designed in two parts and has an axial through-bore (40, 83), the first axial piston part (38) being connected to the armature (22) and being liftable by the second axial piston part (64). When no current is supplied to the coil in the lifted state, the fluidic connection is established between the inlet (26) and the outlet (30) via a gap (67) between the two axial piston parts (38, 64).

Description

 DESCRIPTION

Magnetic pump for an auxiliary unit of a vehicle and method for controlling a magnetic pump for an auxiliary unit

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.

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 Rücksteilen the valve is a filling of the cylinder, since the outlet is closed by the second check valve and the first check valve is lifted from the axial piston due to the resulting in the cylinder due to the backward vacuum. 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 known, for example, from EP 0 288 216 A1. 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 magnetic pump or vibration pump is disclosed in WO 2011/029577 Al. 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, the internal combustion engine may overheat with the corresponding consequential damage.

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.

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.

Characterized in that the axial piston is made in two parts and has an axial through hole, wherein the first axial piston part connected to the armature or is integral with the armature and piston part of the second axial can be lifted, wherein in the off-hook piston portion via a gap between the two axial between the inlet and the outlet, 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. 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 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.

Preferably, 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. 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 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.

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. 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. 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 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.

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.

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 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.

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. 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 flowed through freely 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. An embodiment of a magnetic pump according to the invention is shown in the figure and will be described below. 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. 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.

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 axial piston part 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 in the interior of the core 20 and protrudes from the inlet housing 24 into the outlet housing 28. The first axial piston part 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. At the outlet 30 facing end, the first axial piston part 38 has a bowl-shaped extension 60 against which a prestressed compression spring 62 abuts, the opposite axial end abuts against a second axial piston part 64, the first axial piston part 38 facing end corresponding to the extension 60th of the first axial piston part 38 is formed and on 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 position shown in Figure 1, the second axial piston member 64 is located with a radial extension surface 75 against the radial constriction 70, which serves as a stop 76 for the second axial piston part 64 at. Accordingly, the effective diameter of the first axial piston part 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.

At the outlet 30 facing end of the second axial piston part 64 is hollow cylindrical and protrudes into a cylinder 82 in which the hollow cylindrical part of the second axial piston part 64 is guided and which is arranged radially within the gap 74. Against the open, the outlet 30 facing the end of the second Axialkolbenteils 64 is a through bore 83 of the axial piston member 64 dominant closure body 84 of a first check valve 86 biased by a first spring 88 of the check valve 86, the opposite end against a cylinder 82 axially delimiting constriction 90 abuts, 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. 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. 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.

At this end of the second axial piston part a further annular recess extending in the axial direction is formed, which is formed corresponding to the axial end of the cylinder 82.

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 axial piston part 38 and the first compression spring 38 presses the first axial piston member 38 with the armature 22 in the direction of the inlet 26, so that the gap 67 between the two Axialkolbenteilen 38, 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.

In operation, the solenoid of the magnetic pump between a Teilbestromung and a full energization of the coil 14 is switched back and forth. The height and duration of the Teilbestromung is chosen so that the force of the first compression spring 62 is overcome, so that the first axial piston member 38 abuts against the second Axialkolbenteil 64 and thus the gap 67 between the two axial piston parts 38, 64 via the damping element 66 is closed, so that the two axial piston parts 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. 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.

5 If 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 86 the

10 Axial piston 38, 64 significantly delayed because its spring force for a permanent contact with the axial piston 38, 64 is not sufficient. In this movement, fluid is sucked through the axial through-hole 40, 83 in the cylinder 82 through this negative pressure, so flows through the gap between the first check valve 86 and the axial piston

15 38, 64 in the cylinder 82. In the piston chamber 72, an overpressure is generated by this movement, 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 further funding takes place. The following pressure equalization causes the first check valve to settle

20 86 again 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.

25 By canceling the energization, the two axial piston parts 38, 64 are separated again, since the compression spring 108 pushes the second Axialkolbenteil 64 against the stop 76 and the compression spring 62, the first axial piston member 38 from the second axial piston member 64 pushes away. Accordingly, there is the already described free flow path

30 between the inlet 26 and the outlet 30th All occurring movements due to a current change are attenuated. On the one hand there is a damping of the attacks between the armature 22 and the core 20, the first axial piston member 38 and the second axial piston member 64 and the second 5 Axial piston member 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

10 Another hydraulic damping chamber is effective in the movement of the second axial piston part 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 in the

15 cylinder can be driven and this surface an annular recess 1 10 is formed. In this engages the inlet 26 facing 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 in the recess 1 10 fluid can escape only through gaps and so the

20 motion dampens.

In addition, an undesirable damping effect of the armature movement by compression or negative pressure formation in the space 25 44 is prevented by the transverse bore 42 in the first Axialkolbenteil 38 and the bore 46 in the core 20.

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, 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.

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

P A T E N T A N S P R E C H E 1. A magnetic pump for an auxiliary power unit of a vehicle with
 an inlet (26) and an outlet (30),
 an electromagnet (10) having a translationally movable armature (22), a core (20), a coil (14) and a yoke (16),
 an axial piston (38, 64) movable up and down in a cylinder (82),
 a first check valve (86) which is biased against the axial piston (38, 64),
 a second check valve (96) biased against an outlet opening (92) of the cylinder (82),
 characterized in that
 the axial piston (38, 64) is designed in two parts and has an axial through-bore (40, 83), wherein the first axial piston part (38) is connected to the armature (22) or is made in one piece with the armature (22) and from the second axial piston part ( 64), wherein in the lifted state via a gap (67) between the two Axialkolbenteilen (38, 64) between the inlet (26) and the outlet (30), the fluidic connection.
2. A magnetic pump for an auxiliary unit of a vehicle according to claim 1,
 characterized in that
between the first Axialkolbenteil (38) and the second Axialkolbenteil (64) a compression spring (62) is arranged.
3. A magnetic pump for an auxiliary unit of a vehicle according to any one of claims 1 or 2,
 characterized in that
 the second Axialkolbenteil (64) due to the pressure force of a second, compared to the first compression spring (62) stronger compression spring (108) with complete recovery of the armature (22) abuts against a stop (76) and in the operating positions of the armature (22) Pumping operation against the first Axialkolbenteil (38) is applied.
4. A magnetic pump for an auxiliary unit of a vehicle according to claim 3,
 characterized in that
 the stop (76) is formed on a first insert housing part (68).
5. A magnetic pump for an auxiliary unit of a vehicle according to one of the preceding claims,
 characterized in that
 the first check valve (86) is biased against the second axial piston portion (64) via a first spring (88) and the second check valve (96) is biased against the outlet opening (92) of the cylinder (82) via a second spring (98).
6. A magnetic pump for an auxiliary unit of a vehicle according to one of the preceding claims,
 characterized in that
the first Axialkolbenteil (38) with the armature (22) via a bore (36) in the armature (22) is connected.
7. A magnetic pump for an auxiliary unit of a vehicle according to one of the preceding claims,
 characterized in that
 the effective diameter of the second axial piston part (64) is greater than the effective diameter of the first axial piston part (38).
8. A magnetic pump for an auxiliary unit of a vehicle according to one of the preceding claims,
 characterized in that
 the inlet (26) and the outlet (30) are arranged at axially opposite ends of the magnetic pump, wherein the armature (22) is arranged on the side of the inlet (26) and the check valves (86, 96) and the second axial piston part (64 ) are arranged on the side of the outlet (30).
9. A magnetic pump for an auxiliary unit of a vehicle according to one of the preceding claims,
 characterized in that
 in an outlet housing (28), on which the outlet (30) is formed, a second insert housing part (100) is arranged, in which the cylinder (82) is formed, in which the second axial piston part (64) guided and the first check valve (86 ), wherein the second check valve (96) is loaded against the outlet opening (92) of the cylinder (82), which opens into an outlet space (104) which opens into the outlet (30).
10. A magnetic pump for an auxiliary unit of a vehicle according to claim 9,
 characterized in that
a continuous fluidic connection between a piston chamber (72), in which the first axial piston part (38) protrudes, a clearance (74) surrounding the cylinder (82) and the discharge space (104).
11. A magnetic pump for an auxiliary unit of a vehicle according to claim 5 10,
 characterized in that
 the fluidic connection via openings (80, 106) in the second insert housing part (100) and in the first insert housing part (68) on which between the intermediate space (74) and the piston chamber 10 (72) arranged stop (76) is formed, there is.
12. A magnetic pump for an auxiliary unit of a vehicle according to one of the preceding claims,
 characterized in that
 15 the spring (88) of the first check valve (86) is designed such that the first check valve (86) the second Axialkolbenteil (64), with its movement in the direction of the inlet (26) followed by a delay.
20 13. A magnetic pump for an auxiliary unit of a vehicle according to one of the preceding claims,
 characterized in that
 in the first Axialkolbenteil (38) and the core (20) at the inlet side region in each case a transverse bore (42, 46) is formed.
 25
 14. A magnetic pump for an auxiliary unit of a vehicle according to one of the preceding claims,
 characterized in that
on the second axial piston part (64) in the region of the abutment (76) 30 and / or in the region of the abutment on the first axial piston part (38) and / or between the armature (22) and the core (20) elastic damping elements (48, 66, 78) are arranged.
Magnetic pump for an auxiliary unit of a vehicle according to one of
Claims 9 to 14,
characterized in that
on the second Axialkolbenteil (64) an annular, to the second insert housing part (100) directed recess (110) is formed, which in an axial end of the cylinder (82) immersed in fully towards the outlet (30) displaced armature (22).
Magnetic pump for an auxiliary unit of a vehicle according to one of the preceding claims,
characterized in that
on the side of the inlet (26) an annular recess (34) on an inlet housing (24) of the magnetic pump is formed, in which an annular to the inlet (26) facing corresponding projection (32) of the armature (22) upon complete recovery of the armature (22) dips.
Method for controlling a magnetic pump for an auxiliary unit of a motor vehicle, wherein
an axial piston (38, 64) coupled to an armature (22) of an electromagnet (10) by alternately energizing a coil (14) of the electromagnet (10) in a cylinder (82) to deliver fluid from the inlet (26) to the outlet (30) is moved up and down,
characterized in that
when the coil (14) is de-energized, the armature (22) is pushed to its fully retracted position, in or through the armature (22) or connected thereto formed axial piston (38) in this position of the armature (22) continuously a gap (67) is released, via which a fluidic connection between the inlet (26) and the outlet (30) is produced.
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)

Priority Applications (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)

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

Family

ID=51399623

Family Applications (1)

Application Number Title Priority Date Filing Date
EP14755616.1A Active EP3066343B1 (en) 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

Country Status (4)

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

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102015107207A1 (en) 2015-05-08 2016-11-10 Pierburg Gmbh Magnetic pump for an auxiliary unit of a vehicle
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

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Publication number Priority date Publication date Assignee Title
US1790547A (en) * 1931-01-27 Electbomaauetic pump
US2293684A (en) * 1940-05-13 1942-08-18 Galvin Mfg Corp Electromagnetic pump
US2443344A (en) 1945-05-04 1948-06-15 James F Ekleberry Reciprocating compressor
DE2503241C3 (en) * 1975-01-27 1977-09-08 Nippon Control Ind Co electromagnetic reciprocating pump
JPS5712863B2 (en) * 1977-06-10 1982-03-13
US4274407A (en) * 1979-11-13 1981-06-23 Med Pump, Inc. Fluid injection system
GB8709082D0 (en) 1987-04-15 1987-05-20 Eaton Sa Monaco Electrical fluid pump
JP3777254B2 (en) * 1998-07-29 2006-05-24 日信工業株式会社 Solenoid pump device
DE19937988A1 (en) * 1999-08-11 2001-02-15 Ficht Gmbh & Co Kg Device for conveying and / or spraying flowable media, in particular fluids
DE102007016856A1 (en) * 2007-04-10 2008-10-16 Robert Bosch Gmbh Motorcycle brake device with magnetic pump
DE102008058046A1 (en) * 2008-11-18 2010-05-20 Thomas Magnete Gmbh Reciprocating piston pump for supplying fluid, particularly fuel or fuel additive for internal-combustion engine for fluid supplying system, has supplying area with inlet port and outlet port
EP2475887A1 (en) 2009-09-09 2012-07-18 Vermietungsgemeinschaft Harald Schrott & SYSKO AG GbR Vibrating armature pump
US9004883B2 (en) 2011-04-01 2015-04-14 Gm Global Technology Operations, Llc Low noise high efficiency solenoid pump
US9624922B2 (en) * 2013-02-19 2017-04-18 Wabco Europe Bvba Pressure monitoring device for controlling a compressor

Also Published As

Publication number Publication date
EP3066343B1 (en) 2017-11-29
DE102013112306A1 (en) 2015-05-13
WO2015067384A1 (en) 2015-05-14
US20160281695A1 (en) 2016-09-29
US10151307B2 (en) 2018-12-11

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