WO2016180579A1 - Solenoid pump for an auxiliary unit of a vehicle - Google Patents

Solenoid pump for an auxiliary unit of a vehicle Download PDF

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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
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WO
WIPO (PCT)
Prior art keywords
axial piston
armature
magnetic pump
characterized
auxiliary unit
Prior art date
Application number
PCT/EP2016/057521
Other languages
German (de)
French (fr)
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
Priority to DE102015107207.6A priority Critical patent/DE102015107207A1/en
Priority to DE102015107207.6 priority
Application filed by Pierburg Gmbh filed Critical Pierburg Gmbh
Publication of WO2016180579A1 publication Critical patent/WO2016180579A1/en

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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
    • F04B17/046Pumps 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

Abstract

Solenoid pumps for auxiliary units in vehicles, such as mechanical controllable coolant pumps, comprising: an inlet (24.1; 24.2; 24.3); an outlet (28.1; 28.2; 28.3); an electromagnet (10.1; 10.2; 10.3), which has an armature (20.1; 20.2; 20.3) that can be translated, a core (18.1; 18.2; 18.3), a coil (14.1; 14.2; 14.3), and a yoke (16.1; 16.2; 16.3); an axial piston (38.1; 38.2; 38.3), which can be moved back and forth in a cylinder (56.1; 56.2; 56.3); a first check valve (42.1; 42.2; 42.3), which is preloaded against the axial piston (38.1; 38.2; 38.3); and a second check valve (48.1; 48.2; 48.3), which is preloaded against an outlet opening (55.1; 55.2; 55.3); are known. Previously, in order to relieve a space filled by means of the pump, additional valves had to be provided. According to the invention, in order to achieve such relief even without valves by means of the simplest possible means, the axial piston (38.1; 38.2; 38.3) according to the invention has an axial bore (36.1; 36.2; 36.3) and is designed as a single piece and the solenoid pump has a first sealing element (58.1; 58.2; 58.3) on the axial piston (38.1; 38.2; 38.3), which first sealing element contacts a corresponding first sealing surface (60.1; 60.2; 60.3) on the inner circumference of the cylinder (56.1; 56.2; 56.3) in each position of the armature (20.1; 20.2; 20.3), and has a second sealing element (62.1; 62.2; 62.3), which is lifted off of a corresponding second sealing surface (64.1; 64.2; 64.3) in a backflow position, wherein in the backflow position a fluidic connection exists between the inlet (24.1; 24.2; 24.3) and the outlet (28.1; 28.2; 28.3) via a gap (94.1; 94.2; 94.3) between the second sealing element (62.1; 62.2; 62.3) and the second sealing surface (64.1; 64.2; 64.3).

Description

 DESCRIPTION

Magnetic pump for an auxiliary unit of a vehicle

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.

By alternating energization of the coil with cycle times in the ms range, 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. 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 is created by energizing and Nichtbestromung the coil of the electromagnet.

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 fast Rückström- and no fail-safe function are given. This means, for example, for the application for adjusting an adjusting ring of a coolant pump, that closed by the adjusting ring coolant pump and failure of the magnetic pump, the pressure in the adjustment can be reduced only very slowly by leaks on the magnetic 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. For a quick positioning of the adjusting ring, therefore, a fast backflow must be ensured. An oscillating tank pump with fail-safe function is known from the subsequently published DE 10 2013 112 306 AI. In this pump, the pumping operation between two positions, which are approached at partial or full energized. Without energizing the two axially seated parts of the axial piston are lifted from each other to release a flow path between the inlet and the outlet in this Rückströmposition.

It is therefore an object of the invention to provide a magnetic pump for an auxiliary unit of a vehicle, with the failure or intentional shutdown of the electromagnet, a fast return flow can be made possible by the pump, which the example of the coolant pump to a relief of the adjusting ring and thus to a Maximum delivery of the coolant pump leads. It should also be possible to dispense with additionally controlled valves for releasing the pressure. The number of parts to be mounted should be reduced as much as possible.

This object is achieved by a magnetic pump with the features of the main claim 1.

Characterized in that 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 Rückströmposition, wherein in the Rückströmposition 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. Thus, a Rückströmposition 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.

Preferably, 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.

In addition, 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.

In a preferred embodiment of the invention, 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. In this embodiment can be dispensed with additional components, so that the assembly and manufacture can be done inexpensively.

In this case, the second sealing element is advantageously arranged in the Rückströmposition 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.

In a further embodiment, 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. Correspondingly, in the backflow position in the first section, 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.

In a preferred embodiment, 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 Rückströmposition 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 Rückströmposition. The control for energizing between the two operating end positions is significantly simplified. Due to the axial deformability of the ring, on the one hand, the stop is damped and, on the other hand, energy for the restoration is stored, so that the following movement is accelerated. In an alternative preferred embodiment, 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 Rückströmposition outside the magnetic circuit and are thus freely selectable.

In a further embodiment, the valve member is arranged in the Rückströmposition 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.

In this preferred embodiment, it is advantageous if 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.

Preferably, in this embodiment, 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. Thus, 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 Rückströmposition 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 Rückströmposition.

Furthermore, it is advantageous if the cylinder is arranged in the flow housing radially inside the core of the electromagnet. By such an arrangement, the required axial space is shortened.

In a further advantageous embodiment of the invention, 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.

In a further advantageous embodiment, the fluidic connection between the outlet and the inlet is released in the Rückströmposition 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.

Furthermore, it is advantageous if in the magnetic pump, 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. By such an arrangement, on the one hand, the stop of the armature is damped on the core and on the other hand energy stored in the resilient element, which allows a faster return of the armature.

It is thus a magnetic pump, in particular for an auxiliary unit of a vehicle created, which has a state in which the pump in. In case of failure of the electromagnet or its Nichtbestromung both directions can be flowed through freely, which is realized only by the position of the axial piston or the armature. Thus, it is possible to dispense with an additional valve to be activated for releasing the fluidic connection between inlet and outlet. 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. The proposed valve has a reduced number of components and is easy to assemble.

Three embodiments of the invention magnetic pumps are shown in the figures and are described below.

1 shows a side view of a first embodiment of a magnetic pump according to the invention in a sectional view.

2 shows a side view of a second embodiment of a magnetic pump according to the invention in a sectional view.

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. By energizing the coil 14.1, 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. Furthermore, 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.

In the position shown in Figure 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.

In this first operating position, an interior 86.1 in the flow housing 26.1 between the two check valves 42.1, 48.1 is filled with a fluid. Will now be the coil 14.1 fully energized, so that the electromagnetic force exceeds the sum of the spring forces of the first compression spring 70.1 and the second compression spring 72.1, the armature 20.1 is moved to the core 18.1, wherein the energy stored in the resilient element 76.1 by the compression energy is released to accelerate this movement. This means that in each case at the end of the movement, a greater force is applied to the compression of the resilient element 76.1 and the stored energy is released at the beginning of the subsequent movement. 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. In the opposite direction, a fluid flow is prevented by the first sealing element 58.1.

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. As a result, fluid flows from the inlet 24.1 via the through-bore 34.1 in the armature 20.1 and the axial bore 36.1 in the axial piston 38.1 into the interior 86.1. In order to prevent hydraulic pressures in the intermediate spaces 90.1 from being raised or released due to the movements of the armature 20.1 and the axial piston 38.1, which would hinder the free movement, a plurality of transverse bores 92.1 are arranged on the axial piston 38.1 via which these intermediate spaces 90.1 are located within the Solenoid valve, which are arranged closer to the electromagnet 10.1 than the interior 86.1, connected to each other and to the inlet 24.1.

To ensure, for example, when using this magnetic pump as a hydraulic pressure generator for controlling a slider of a mechanical water pump of a vehicle that the pump continues to run at maximum power in case of power failure, 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. As a result, a gap 94.1 is released between the axial piston 38.1 and the cylinder 56.1 in the region of the sealing surface 64.1, via which there now exists a fluidic connection between the inlet 24.1 and the outlet 28.1, whereby a return flow of the fluid from the outlet 28.1 to the inlet 24.1 corresponding to the adjacent Pressure differences is possible. This flow takes place from the outlet 28.1 between the outer housing 68.1 and the flow housing 26.1, then via the transverse bore 66.1 in the flow housing 26.1 along the gap 94.1 and via the transverse bores 92.1 to the axial bore 36.1 and along the through-bore 34.1 to the inlet 24.1. For the description of the exemplary embodiment shown in FIG. 2, the same main reference symbols with adapted additional reference symbols are used below for components having the same effect. The embodiment according to 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.

In the illustrated position, 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.

If now switched to full energization of the coil 16.2, 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. In the interior 86.2 between the two check valves 42.2, 48.2 Here too, 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.

Shortly before the armature 20.2 comes to rest on the core 18.2, 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.

When switching to partial energization of the axial piston 38.2 and with it the armature 20.2 is moved back by the spring force of the first compression spring 70.2 and at the beginning of the movement by the stored energy of the resilient element 76.2 in the first operating position. In this case, the fluid present in the interior 86.2 is compressed until the second check valve 48.2 releases the outlet opening 55.2 as a result of the resulting pressure and the fluid flows from the interior 86.2 to the outlet 28.2. A reverse flow is again prevented by the first sealing element 58.2 on the outer circumference of the axial piston 38.2 and the sealing surface 60.2 corresponding thereto with the inner circumference of the cylinder 56.2 of the flow housing 26.2.

If there is a failure of the solenoid 10.2, 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. However, before the armature 20.2 reaches a wall 108.2 of the flow housing 26.2, by means of which its axial movement is limited, 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,

48.2 are bypassable. 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.

In this return flow position, a fluidic connection from the outlet 28.2 via a gap 94.2 between the inner wall of the bore 112.2 and the actuator 110.2, and the space 114.2, transverse bores 92.2 in the axial piston 38.2 and through bores 122.2 in the armature 20.2 to the inlet 24.2 is prepared accordingly. These transverse and through holes 92.2, 122.2 simultaneously serve to produce the pressure equalization between the two axial sides of the armature 20.2.

From this second embodiment, 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,

48.3 and the first sealing element 58.3 in the form of a sealing ring and the first sealing surface 60.3 are formed, are arranged within the core 18.3 and thus the direction of action of the electromagnet was again reversed 10.3. In addition, 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.

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.

In the illustrated position, 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.

If the coil 16.3 is now switched to full energization, 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. In the interior 86.3 between the two non-return valves 42.3, 48.3, 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 Teilbestromung.

When re-switching to partial energization of the coil 16.3 of the axial piston 38.3 and with it the armature 20.3 is moved back by the spring force of the first compression spring 70.3 and at the beginning of the movement by the stored energy of the resilient element 76.3 in the first operating position. This in turn creates a negative pressure in the interior 86.3, so that the first check valve 42.3 opens and via the axial bore 36.3 of the axial piston 38.3 fluid in the Inner space 86.3 is pulled until a force equilibrium is present on the valve body 44.3 and the check valve 42.3 closes again.

By successive switching between partial energization and full energization correspondingly creates a promotion of the fluid through the pump.

In case of failure or intentional switching off of the electromagnet 10.3, 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. This creates a fluidic connection between the inlet 24.3 and the outlet 28.3 via the axial bore 36.3, transverse bores 92.3 in the axial piston 38.3 and the space 114.3, and the through bores 122.3 at the armature 20.3 and from there via the gap 94.3, in the bore 112.3 between the inner wall and the actuating member 110.3 and between serving as a second sealing element 62.3 valve member 116.3 and serving as a second sealing surface 64.3 valve seat 118.3, is released.

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. At the same time, this function of resetting the armature in its Rückströmposition can also be used as a fail-safe function with appropriate use of the solenoid. Thus it can be dispensed with a separate valve. 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.

It should be clear that the scope of the main claim is not limited to the described embodiments, but further structural modifications are possible.

Claims

PAT E NTAN S P RU C H E
Magnetic pump for an auxiliary unit of a vehicle with
an inlet (24.1; 24.2; 24.3) and an outlet (28.1; 28.2;
28.3),
an electromagnet (10.1; 10.2; 10.3), a translationally movable armature (20.1; 20.2; 20.3), a core (18.1; 18.2; 18.3), a coil (14.1; 14.2; 14.3) and a yoke (16.1; 16.2; 16.3 ) having,
an axial piston (38.1; 38.2; 38.3) movable up and down in a cylinder (56.1; 56.2; 56.3),
a first check valve (42.1; 42.2; 42.3) which is biased against the axial piston (38.1; 38.2; 38.3),
a second check valve (48.1; 48.2; 48.3) which is biased against an outlet opening (55.1; 55.2; 55.3),
characterized in that
the axial piston (38.1; 38.2; 38.3) has an axial bore (36.1; 36.2; 36.3) and is integrally formed and the magnetic pump has a first sealing element (58.1; 58.2; 58.3) on the axial piston (38.1; 38.2; Position of the armature (20.1, 20.2, 20.3) abuts against a corresponding first sealing surface (60.1, 60.2, 60.3) on the inner circumference of the cylinder (56.1, 56.2, 56.3) and a second sealing element (62.1, 62.2, 62.3), which of a corresponding second sealing surface (64.1; 64.2; 64.3) is lifted off in a backflow position, wherein in the backflow position, a gap (94.1; 94.2; 94.3) between the second sealing element (62.1; 62.2; 62.3) and the second sealing surface (64.1; 64.2; 64.3) there is a fluidic connection between the inlet (24.1; 24.2; 24.3) and the outlet (28.1; 28.2; 28.3).
Magnetic pump for an auxiliary unit of a vehicle according to claim characterized in that
 the magnetic pump has a first compression spring (70.1; 70.2; 70.3) via which the axial piston (38.1; 38.2; 38.3) is loaded in the direction of a first operating position, wherein the movement caused by the spring force of the first compression spring (70.1; 70.2; 70.3) of the axial piston (38.1; 38.2; 38.3) by a stop (84.1; 100.
2; 131.3) is limited.
3. A magnetic pump for an auxiliary unit of a vehicle according to any one of claims 1 or 2,
 characterized in that
 the magnetic pump has a second compression spring (72.1; 72.2; 72.3) which has a lower spring force than the first compression spring (70.1; 70.2; 70.3) and over which the second sealing element (62.1; 62.2; 62.3) is loaded in the opening direction.
4. A magnetic pump for an auxiliary unit of a vehicle according to one of the preceding claims,
 characterized in that
 the second sealing element (62.1) is formed on the outer circumference of the axial piston (38.1) and the second sealing surface (64.1) is formed on the inner circumference of the cylinder (56.1).
5. A magnetic pump for an auxiliary unit of a vehicle according to claim 4,
 characterized in that
 the second sealing element (62.1) is arranged in the backflow position axially outside the sealing surface (64.1) and the gap (94.1) between the cylinder (56.1) and the axial piston (38.1) is released.
6. A magnetic pump for an auxiliary unit of a vehicle according to one of the preceding claims, characterized in that
 the two sealing surfaces (60.1, 64.1) are formed on the inner circumference of the cylinder (56.1), which is graduated, has a transverse bore (66.1) and is surrounded by an outer housing (68.1), which in a first section, which from the outlet (28.1 ) to the transverse bore (66.1) extends radially to the cylinder (56.1) is arranged and in the following, closer to the inlet (24.1) arranged second portion sealingly surrounds the cylinder (56.1), wherein the second sealing surface (64.1) radially within the second axial portion is arranged.
7. A magnetic pump for an auxiliary unit of a vehicle according to one of claims 2 to 6,
 characterized in that
 the first compression spring (70.1) is clamped between a support surface (74.1) and an axially resilient element (76.1), which in both operating positions is tensioned in the direction of a stop (84.1, 88.1) and against a shoulder (78.1) of the axial piston (38.1; 38.2) bears against one of the stops (84.1) in the return flow position and is axially spaced from the axial piston (38.1; 38.2; 38.3).
8. A magnetic pump for an auxiliary unit of a vehicle according to one of claims 1 to 3,
 characterized in that
the second sealing element (62.2; 62.3) is formed by a valve member (116.2; 116.3) which corresponds to a sealing surface (64.2; 64.3) designed as a valve seat (118.2; 118.3) which is located at one axial end of a bore (112.2; 112.3). in a flow housing (26.2, 26.3) is formed.
9. A magnetic pump for an auxiliary unit of a vehicle according to one of claims 1 to 3 or 8,
 characterized in that
 the valve member (116.2, 116.3) in the Rückströmposition axially spaced from the valve seat (118.2, 118.3) is arranged and the gap (94.2, 94.3) between the valve member (116.2, 116.3) and the valve seat (118.2, 118.3) and along the bore ( 112.2; 112.3) in the flow housing (26.2; 26.3) is released.
10. A magnetic pump for an auxiliary unit of a vehicle according to claim 9,
 characterized in that
 the second compression spring (72.2, 72.3) in the backflow position via an actuating member (110.2, 110.3), which at least partially in the bore (112.2, 112.3) in the flow housing (26.2, 26.3) is disposed against the armature (20.2; Valve member (116.2; 116.3) loaded.
11. A magnetic pump for an auxiliary unit of a vehicle according to one of claims 8 to 10,
 characterized in that
 the armature (20.2; 20.3) is mounted in the flow housing (26.2; 26.3) and axially displaceable on the axial piston (38.1; 38.2; 38.3), wherein a shoulder (102.2; 102.3) is formed on the axial piston (38.1; 38.2; with which the axial piston (38.1, 38.2, 38.3) rests in the operating positions against the armature (20.2, 20.3).
12. A magnetic pump for an auxiliary unit of a vehicle according to one of claims 8 to 11,
 characterized in that
the axial piston (38.2; 38.3) rests against a stop (100.2; 134.3) in the return flow position by the first compression spring (70.2, 70.3).
13. A magnetic pump for an auxiliary unit of a vehicle according to any one of claims 8 to 12,
 characterized in that
 the cylinder (56.3) in the flow housing (26.3) is arranged radially inside the core (18.3) of the electromagnet (10.3).
14. A magnetic pump for an auxiliary unit of a vehicle according to one of claims 8 to 13,
 characterized in that
 the outlet (28.3) is arranged at the axial end of the flow housing (26.3) opposite the armature (20.3) and radially inside the core (18.3).
15. A magnetic pump for an auxiliary unit of a vehicle according to one of claims 1 to 3 or 8 to 14,
 characterized in that
 in the return flow position, the fluidic connection between the outlet (28.3) and the inlet (24.3) is released via a space (114.3) in which the armature (20.3) is slidably disposed, wherein at least one transverse bore (92.3) is provided on the axial piston (38.3) and on the armature (20.3) through holes (122.3) and the actuating member (110.3) are formed.
16. A magnetic pump for an auxiliary power unit of a vehicle according to one of claims 1 to 3 or 8 to 15,
 characterized in that
 in the magnetic pump a resilient element (76.2, 76.3) is arranged, which is arranged axially between the armature (20.2; 20.3) and a ring (104.2; 104.3) and in the operating position in which the armature (20.2; 20.3) and the Ring (104.2, 104.3) on the core (18.2; 18.3) rest, is compressed.
PCT/EP2016/057521 2015-05-08 2016-04-06 Solenoid pump for an auxiliary unit of a vehicle WO2016180579A1 (en)

Priority Applications (2)

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DE102015107207.6A DE102015107207A1 (en) 2015-05-08 2015-05-08 Magnetic pump for an auxiliary unit of a vehicle
DE102015107207.6 2015-05-08

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP16714893.1A EP3295026A1 (en) 2015-05-08 2016-04-06 Solenoid pump for an auxiliary unit of a vehicle

Publications (1)

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

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ID=55697189

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PCT/EP2016/057521 WO2016180579A1 (en) 2015-05-08 2016-04-06 Solenoid pump for an auxiliary unit of a vehicle

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DE (1) DE102015107207A1 (en)
WO (1) WO2016180579A1 (en)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
IT201800003069A1 (en) * 2018-02-27 2019-08-27 Elbi Int Spa Vibration pump with improved implementation

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EP0288216A1 (en) * 1987-04-15 1988-10-26 Eaton S.A.M. Electrical fluid pump
DE102005048765A1 (en) * 2005-10-10 2007-04-12 Aweco Appliance Systems Gmbh & Co. Kg Oscillating anchor pump used in household appliances, e.g. coffee machines comprises a sliding surface formed as a sealing surface for sealing the cylinder of a pump housing during axial displacement of a plunger using a sealing element
DE102008013440A1 (en) * 2008-03-10 2009-09-17 Thomas Magnete Gmbh Magnetically actuated reciprocating pump for delivering and exact dosing of hydraulic fluid from inlet to outlet area of pump, has hollow chambers of pump that are filled with fluid in currentless condition
WO2011029577A1 (en) * 2009-09-09 2011-03-17 Rudolf Lonski Vibrating armature pump

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AT235000T (en) * 1998-05-15 2003-04-15 Rolland Versini Motor pump with axial flow, with integrated flow meter and pressure switch
JP4186256B2 (en) * 1998-06-17 2008-11-26 株式会社デンソー Solenoid valve integrated solenoid pump
DE102008010073B4 (en) * 2008-02-19 2010-10-21 Thomas Magnete Gmbh System and method for metering a fluid
DE202008007146U1 (en) * 2008-05-27 2008-08-14 Lincoln Gmbh Pump element
DE102013112306A1 (en) 2013-11-08 2015-05-13 Pierburg Gmbh Magnetic pump for an auxiliary unit of a vehicle and method for controlling a magnetic pump for an auxiliary unit

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EP0288216A1 (en) * 1987-04-15 1988-10-26 Eaton S.A.M. Electrical fluid pump
DE102005048765A1 (en) * 2005-10-10 2007-04-12 Aweco Appliance Systems Gmbh & Co. Kg Oscillating anchor pump used in household appliances, e.g. coffee machines comprises a sliding surface formed as a sealing surface for sealing the cylinder of a pump housing during axial displacement of a plunger using a sealing element
DE102008013440A1 (en) * 2008-03-10 2009-09-17 Thomas Magnete Gmbh Magnetically actuated reciprocating pump for delivering and exact dosing of hydraulic fluid from inlet to outlet area of pump, has hollow chambers of pump that are filled with fluid in currentless condition
WO2011029577A1 (en) * 2009-09-09 2011-03-17 Rudolf Lonski Vibrating armature pump

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