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 assemblyInfo
- 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
- magnetic pump
- inlet
- 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
Links
- 238000000034 method Methods 0.000 title claims description 8
- 239000012530 fluid Substances 0.000 claims abstract description 21
- 238000005086 pumping Methods 0.000 claims abstract description 7
- 230000006835 compression Effects 0.000 claims description 20
- 238000007906 compression Methods 0.000 claims description 20
- 238000013016 damping Methods 0.000 claims description 16
- 238000011084 recovery Methods 0.000 claims description 3
- 230000000712 assembly Effects 0.000 abstract 1
- 238000000429 assembly Methods 0.000 abstract 1
- 239000002826 coolant Substances 0.000 description 9
- 238000007789 sealing Methods 0.000 description 3
- 230000015572 biosynthetic process Effects 0.000 description 2
- 230000001276 controlling effect Effects 0.000 description 2
- 230000003111 delayed effect Effects 0.000 description 2
- 238000005755 formation reaction Methods 0.000 description 2
- 238000004519 manufacturing process Methods 0.000 description 2
- 230000035939 shock Effects 0.000 description 2
- 230000002238 attenuated effect Effects 0.000 description 1
- 238000002485 combustion reaction Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000003825 pressing Methods 0.000 description 1
- 230000001105 regulatory effect Effects 0.000 description 1
- 230000001629 suppression Effects 0.000 description 1
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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B17/00—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
- F04B17/03—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors
- F04B17/04—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors using solenoids
- F04B17/042—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors using solenoids the solenoid motor being separated from the fluid flow
- F04B17/044—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors using solenoids the solenoid motor being separated from the fluid flow using solenoids directly actuating the piston
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
- F04B53/10—Valves; Arrangement of valves
- F04B53/12—Valves; Arrangement of valves arranged in or on pistons
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
- F04B53/14—Pistons, piston-rods or piston-rod connections
Definitions
- the invention relates to a magnetic pump for an auxiliary unit of a vehicle having an inlet and an outlet, an electromagnet having a translationally movable armature, a core, a coil and a yoke, an axial piston which is movable up and down in a cylinder, a first check valve, which is biased against the axial piston and a second check valve, which is biased against an outlet opening of the cylinder and a method for controlling a magnetic pump for an auxiliary unit of a motor vehicle, wherein a coupled to an armature of an electromagnet axial piston by an alternating energization of the Spool is moved up and down in a cylinder for conveying a fluid from the inlet to the outlet.
- Such magnetic pumps are used, for example, to provide the pressure for the hydraulic adjustment of a valve spool of a coolant pump driven by a belt pulley, the volume flow of which can be regulated in this way.
- an armature of the electromagnet and with this armature an axial piston, which has an axial through-hole, in a cylinder moves up and down in these pumps.
- the through-bore is closed at its end facing the outlet by a check valve, which is also arranged in the cylinder.
- the ejection movement takes place against another check valve which bears against an outlet of the cylinder.
- Such an electric fluid pump is known, for example, from EP 0 288 216 A1.
- 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.
- 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.
- a fail-safe position for example, for the application of a controlled via a slider coolant pump is created.
- a compression spring is arranged between the first Axialkolbenteil and the second Axialkolbenteil, which ensures that the armature is in its fully retracted position in case of failure of the electromagnet and on the other hand dampens the stop of the two Axialkolbenforce upon movement of the armature from this position.
- the second Axialkolbenteil is due to the compressive force of a second compared to the first compression spring, stronger compression spring at full return of the armature against the stop and in the operating positions during pumping operation of the armature against the first Axialkolbenteil. This ensures that when moving from the fully retracted position of the armature first, the gap between the first Axialkolbenteil and the second Axialkolbenteil is closed and then the axial piston is displaced as a unit during the actual pumping movement.
- the first check valve is biased by a first spring against the second Axialkolbenteil and is moved with this in the direction of the outlet and the second check valve is biased by a second spring against the outlet opening of the cylinder. So on the one hand, a sufficient pressure build-up in the ejection movement ensured and on the other hand allows subsequent filling of the cylinder in pumping operation.
- the first Axialkolbenteil is advantageously connected via a bore in the armature to the armature, whereby the joint movement is ensured. Nevertheless, the structure and the assembly is easy, since the attachment can be made by screwing or pressing and only the first Axialkolbenteil must be performed.
- the effective diameter of the second Axialkolbenteils is greater than the effective diameter of the first Axialkolbenteils.
- the inlet and the outlet are arranged at axially opposite ends of the magnetic pump, wherein the armature is arranged on the side of the inlet and the check valves and the second Axialkolbenteil are arranged on the side of the outlet.
- An advantageous embodiment of the invention provides that in a discharge housing, a second insert housing part is arranged, in which the cylinder is formed, in which the second Axialkolbenteil out and the first check valve is arranged, wherein the second check valve is loaded against an outlet opening of the cylinder, which opens into an outlet space, which opens into the outlet.
- this allows the fluidic connection to be established between the inlet and the outlet.
- 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.
- 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.
- 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.
- 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.
- the annular recess serves as a hydraulic damping chamber.
- FIG. 1 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.
- the 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.
- 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.
- an elastic damping element 48 is attached to the core 20 on its surface facing the armature 22.
- the inlet housing 24 is attached with the interposition of a sealing ring 50 on the return ring 18, on the axially opposite side of a further sealing ring 52 is arranged, which seals a gap between the bobbin 12 and the return ring 18, so that no fluid can reach the coil 14.
- the core 20 On the axially opposite side of the electromagnet 10, the core 20 has a radial extension 54, on the axially on both sides more sealing rings 56, 58 are arranged, on the one hand the gap to the outlet housing 28 which is secured to the core 20 and on the other hand the gap to the bobbin 12 seal.
- the first 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.
- a first Einlegegeophuseteil 68 is arranged with a radial constriction 70, through which the outlet housing 28 is divided into a piston chamber 72 and a gap 74.
- the second axial piston 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.
- an elastic damping element 78 is arranged in the area of the stop 76 in turn.
- 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.
- 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.
- a second insert housing part 100 is arranged, which forms the cylinder 82 and its axial boundary wall 102 facing the outlet 30 separates the space 74 from an outlet space 104, which leads to the outlet 30 and in which the second check valve 96 is arranged.
- this boundary wall 102 in turn, at least one opening 106 is formed, via which there is a continuous fluidic connection between the intermediate space 74 and the outlet space 104.
- a compression spring 108 which is stronger than the compression spring 62 and which surrounds the cylinder 82.
- This compression spring 108 is supported with its first axial end against the intermediate wall 102 and with its other axial end against the extension surface 75 of the second Axialkolbenteils 64 so that it is loaded in the direction of the first Axialkolbenteils 38.
- the inlet 26 is fluidically connected to the outlet 30 via the through-bore 40, the gap 67, the piston space 72, the openings 80, 106 of the inserts 68, 100 and the outlet space 104.
- the solenoid of the magnetic pump between a sectionbestromung and a full energization of the coil 14 is switched back and forth.
- the height and duration of the Operabestromung 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 Operabestromung because their force is greater than that of the electromagnet 10 at Generalbestromung.
- 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.
- 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.
- the axial piston 38, 64 is moved as a unit in the direction of the outlet 30.
- 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.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Electromagnetic Pumps, Or The Like (AREA)
Abstract
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE201310112306 DE102013112306A1 (en) | 2013-11-08 | 2013-11-08 | Magnetic pump for an auxiliary unit of a vehicle and method for controlling a magnetic pump for an auxiliary unit |
PCT/EP2014/067247 WO2015067384A1 (en) | 2013-11-08 | 2014-08-12 | Magnet pump for an auxiliary assembly of a vehicle, and method for controlling a magnet pump for an auxiliary assembly |
Publications (2)
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) |
Families Citing this family (7)
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 |
DE102020201813A1 (en) | 2020-02-13 | 2021-08-19 | Magna Pt B.V. & Co. Kg | Oscillating piston pump arrangement and method for operating an oscillating piston pump arrangement |
CN112523986A (en) * | 2020-11-09 | 2021-03-19 | 广西玉柴机器股份有限公司 | Water pumping device of vehicle cooling system |
US20230400017A1 (en) * | 2022-06-14 | 2023-12-14 | Hydac Fluidtechnik Gmbh | Pump device |
Family Cites Families (14)
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 Industrial Co., Ltd., Tokio | ELECTROMAGNETIC PISTON PUMP |
JPS5415504A (en) * | 1977-06-10 | 1979-02-05 | Daisan Kogyo | Solenoid plunger pump |
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 |
WO2011029577A1 (en) | 2009-09-09 | 2011-03-17 | Rudolf Lonski | 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 |
-
2013
- 2013-11-08 DE DE201310112306 patent/DE102013112306A1/en not_active Withdrawn
-
2014
- 2014-08-12 WO PCT/EP2014/067247 patent/WO2015067384A1/en active Application Filing
- 2014-08-12 US US15/034,181 patent/US10151307B2/en active Active
- 2014-08-12 EP EP14755616.1A patent/EP3066343B1/en active Active
Also Published As
Publication number | Publication date |
---|---|
WO2015067384A1 (en) | 2015-05-14 |
EP3066343B1 (en) | 2017-11-29 |
US20160281695A1 (en) | 2016-09-29 |
US10151307B2 (en) | 2018-12-11 |
DE102013112306A1 (en) | 2015-05-13 |
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