EP3022442B1 - Piston pour une pompe à armature oscillante - Google Patents

Piston pour une pompe à armature oscillante Download PDF

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Publication number
EP3022442B1
EP3022442B1 EP14728923.5A EP14728923A EP3022442B1 EP 3022442 B1 EP3022442 B1 EP 3022442B1 EP 14728923 A EP14728923 A EP 14728923A EP 3022442 B1 EP3022442 B1 EP 3022442B1
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EP
European Patent Office
Prior art keywords
piston
armature
pressure
pressure piston
pump
Prior art date
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Application number
EP14728923.5A
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German (de)
English (en)
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EP3022442A1 (fr
Inventor
Hubert Ott
Norbert Helbling
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Sysko AG
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Sysko AG
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Publication of EP3022442A1 publication Critical patent/EP3022442A1/fr
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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
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B17/00—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
    • F04B17/03—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors
    • F04B17/04—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors using solenoids
    • F04B17/046—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors using solenoids the fluid flowing through the moving part of the motor

Definitions

  • the invention relates to a piston for a vibration tank pump and a vibration tank pump and a method for producing a piston for a vibration tank pump.
  • a piston for an oscillating armature pump in particular for a household appliance with a vibrating armature pump, which is provided for conveying a fluid under the action of a counter-pressure, with a pressure piston element and a separate from the pressure piston element, at least one force direction fixedly coupled to the pressure piston element anchor element, at least partially made of a magnetizable material known.
  • a piston for an oscillating armature pump which is provided for conveying a fluid under the action of a counter-pressure 15, with a pressure piston element and a separate from the pressure piston element, for at least one direction of force fixed to the pressure piston element anchor element, at least partially made of a magnetizable Material exists.
  • the EP 0 288 216 A1 teaches in particular that the pressure piston element is inserted exclusively into an end region of an anchor element and the anchor element is fixed by 20 crimping of the pressure piston element in the end region of the anchor element.
  • the anchor element In an area in the flow direction from an inlet to an outlet in front of the end region, the anchor element has an inner bore with an inner diameter which is deliberately chosen substantially larger than an inner diameter of an inner bore of the anchor element - this in particular due to an objective, for a given advantageous mass of Anchor element to solve a given task, namely to avoid vibrations caused by unwanted currents.
  • the object of the invention is, in particular, to reduce manufacturing costs and weight for a vibration tank pump. Furthermore, the object of the invention is, in particular, to provide a simple and secure connection of the pressure piston element and the anchor element.
  • the object is achieved by the features of the independent claims, while advantageous embodiments and modifications of the invention can be taken from the dependent claims.
  • the invention relates to a piston for an oscillating armature pump, in particular for a domestic appliance with a vibrating armature pump, which is provided for conveying a fluid under the action of a counter-pressure, with a pressure piston element and a separate from the pressure piston element, for at least one direction of force fixed to the pressure piston element coupled anchor element, which consists at least partially of a magnetizable material.
  • the anchor element is attached to the pressure piston element.
  • a "piston with a pressure piston element and an armature element” should be understood as meaning, in particular, an at least two-part piston which has at least one component which is provided for displacing the fluid and a component which interacts with a magnet coil to generate an actuating force is provided has.
  • firmly coupled at least in one direction of force is to be understood in particular that the anchor element is at least for a direction corresponding to an actuation force generated by the solenoid coil, rigidly coupled to the pressure piston element.
  • the anchor element is fixedly coupled to the pressure piston element only for one direction of force.
  • the pressure piston element forms a receptacle located radially inside the anchor element, which is at least substantially intended to radially position the anchor element, whereas an axial holding force is not provided by the inner receptacle becomes.
  • the pressure piston element for the anchor element forms a receptacle which has a direction of attachment directed along the direction of the force.
  • the anchor element can be easily mounted, since it only has to be plugged onto the receptacle formed by the pressure piston element.
  • forces acting on the anchor element can be supported well in relation to the pressure piston element, whereby in particular a high degree of operational reliability can be ensured.
  • a "direction of insertion directed along a direction of force" is to be understood in particular as meaning that the anchor element is attached to the pressure piston element during assembly along a direction corresponding to a direction which has a force acting on the anchor element during operation.
  • the receptacle is provided at least substantially for the radial positioning of the anchor element.
  • the recording can be optimized only on the radial positioning, whereby the recording can be designed structurally simple, especially in the form of a circular cylinder.
  • the recording is not intended to transmit axially acting forces, but in principle it is possible that are transmitted by friction effects or similar axially acting forces, which, however, are much smaller than on
  • a radial fit between the receptacle and the anchor element can in particular be designed such that a force that can be transmitted through the inner receptacle is smaller in the axial direction than a weight force acting on the anchoring element. that a clearance is provided or at least permitted between the receptacle and the anchoring element, as a result of which the force which can be transmitted by the receptacle located on the inside is almost zero in the axial direction.
  • the pressure piston element has an outer contour provided for receiving the armature element and / or the armature elements has an inner contour provided for arrangement on the pressure piston element with a surface that is non-deformed in the axial direction.
  • a “provided for receiving the anchor element outer contour” and a “provided for arrangement on the pressure piston element inner contour” is in particular a shape of the pressure piston element and the anchor element in a region in which the pressure piston element and the anchor element are arranged nested in the assembled state understood ,
  • the pressure piston element for the anchor element forms a stop which is provided for supporting an actuating force acting on the anchor element.
  • a form-fitting coupling between the anchor element and the pressure piston element can be produced, as a result of which the actuating force acting on the anchor element can be easily and securely applied to the Pressure piston element can be transferred.
  • a "stop" is to be understood in particular a shape adjacent to the receptacle for the anchor element shaping, which is at least substantially provided to provide a positive connection in the axial direction and thereby to transmit the actuation force acting on the anchor element to the pressure piston element.
  • the stop limits a Aufsteckianae for the anchor element.
  • This allows a particularly good fixation can be achieved with easy installation.
  • the anchor member has an end face which rests positively in the mounted state on the stop.
  • the anchor element can be constructed structurally simple in the form of a sleeve or a tube, whereby in particular production costs for the anchor element can be kept low.
  • the pressure piston element completely penetrate the anchor element.
  • the anchor element can be securely fixed on the pressure piston element.
  • the pressure piston element is designed as a plastic part.
  • the pressure piston element can be easily and inexpensively manufactured.
  • the pressure piston element is designed as an injection-molded component.
  • the pressure piston element can be produced particularly inexpensively, in particular if it has a complex geometry. In principle, however, an embodiment as a deep-drawn component is also conceivable.
  • the pressure piston element has at least one pressure equalization channel.
  • pressure equalization can be easily established between different areas around the pressure piston element.
  • the pressure equalization channels can be particularly easily provided in the pressure piston element when the pressure piston element has a pressure equalization channel.
  • the anchor element is designed as a sheet metal bent part, which is rolled in the form of a sleeve.
  • the anchor element can be easily provided with any, in particular larger, inner diameter and / or outer diameter, without thereby increasing a Materialauschuss.
  • the anchor element can thereby be provided with a small additional cost with an outer diameter which is larger than an outer diameter of comparable pistons.
  • a magnetic field generated by a magnetic coil can be better penetrated by the anchor element, whereby the magnetic coil can be made smaller.
  • the additional costs associated with the enlargement of the outer diameter of the piston can be compensated again, whereby a total of manufacturing costs for a vibration pump can be reduced.
  • a design as a "bending component” is to be understood in particular that the anchor element is formed by forming a semi-finished by a plastic forming force is exerted on the semi-finished, which causes a permanent deformation.
  • bending member is meant in particular no extruded component, which is produced by forming by means of a die through which a blank is pressed through, such as a seamless tube.
  • Rolled is to be understood in particular as meaning that the anchor element is formed from a sheet which is provided along a transverse extension direction with a substantially equal curvature over an entire circumference, whereby the anchor element after its formation in a cross section in the form of a circular ring segment is formed, which has a circumferential extent of at least 270 °, preferably at least 315 ° and more preferably of at least almost 360 °.
  • 360 ° is to be understood in particular that the remaining after rolling longitudinal slot which extends along a longitudinal axis of the anchor member, an angle smaller than 1 °, all angles being related to a central axis of the anchor element.
  • a magnetic coil of the oscillating piston pump has a coil diameter which is at most a factor of 3.0 larger than an outer diameter of the anchor element.
  • the coil diameter is at most a factor of 3.0 larger than the outer diameter of the anchor member, a particularly good coupling can be achieved, whereby a number of windings of the magnetic field coil can be reduced.
  • copper for producing the magnetic field coil can be saved, whereby costs can be reduced.
  • a better cooling of the solenoid can be achieved with the enlarged coil diameter, which in particular for a coffee machine a vibrating piston pump can be provided which can provide a nearly constant pumping power even with a rapidly consecutive number of coffee purchases, as in particular a temperature increase and thus an increase an inner resistance of the oscillating armature pump can be kept low by the improved cooling.
  • the factor is higher than 3.0.
  • the factor can also be smaller, in particular if the oscillating piston pump is designed as a high-pressure pump, where the factor can be, for example, less than 2.7 or less than 2.5.
  • a coil diameter should be understood to mean, in particular, an outer diameter of a coil housing.
  • a "coil housing” is to be understood in particular a preferably cylindrical housing of the magnetic coil, which Copper windings of the coil encloses.
  • an air gap can be provided between the copper windings and the coil housing.
  • the coil housing is formed by the copper windings are encapsulated.
  • the coil has a winding diameter, the highest by a factor of 2.5 larger is the outer diameter of the anchor element.
  • a “winding diameter” should be understood to mean, in particular, a maximum diameter of the copper windings.
  • a “low-pressure pump” is to be understood in particular as an oscillating piston pump which is intended to provide a pressure of at most 5 bar, preferably at most 3 bar. An operating range in which a low-pressure pump provides usable pumping power lies in particular in a pressure range between 1.5 bar and 2.0 bar.
  • a “high-pressure pump” is to be understood in particular as an oscillating piston pump which is provided to provide a pressure of at least 10 bar, preferably at least 14 bar. An operating range in which a high-pressure pump provides usable pump power lies in particular in a pressure range between 10 bar and 14 bar.
  • a method for producing a piston for a vibrating armature pump which is provided for conveying a fluid under the action of a counter-pressure, with a pressure piston element and a separate from the pressure piston element executed, for at least one force direction fixed to the pressure piston element coupled anchor element, at least partially a magnetizable material, in which the anchor element is plugged onto the pressure piston element proposed.
  • the FIGS. 1 to 5 show a vibration pump for a household appliance.
  • the oscillating armature pump shown is intended to convey a liquid, for example water, under a pressure of at least 10 bar.
  • the oscillating armature pump has a minimum delivery rate, which is adapted to the domestic appliance for which the oscillating armature pump is provided.
  • a maximum pressure that the vibration tank pump can provide may be limited.
  • When used with a coffee machine oscillating armature pump may for example be designed to provide at least a minimum flow of at least 190 ml / min at a back pressure of 12 bar, the maximum pressure is limited to about 19.5 bar.
  • the vibration pump comprises a solenoid 18a with a coil housing 19a and a piston 10a.
  • the oscillating armature pump comprises a pump 20a acting on the piston 10a.
  • the oscillating armature pump comprises a spool housing 19a with the magnetic coil 18a passing through piston guide 38a, which encloses a pump interior, in which the piston 10a is guided axially movable.
  • the piston guide 38a is executed in the illustrated embodiment separately from the coil housing 19a.
  • the piston guide 38a itself can be multi-part be educated.
  • the pump spring 20a is supported between the piston guide 38a fixedly connected to the coil case 19a and the piston 10a.
  • the magnetic coil 18a is provided to generate a magnetic field that partially penetrates the pump interior.
  • the oscillating armature pump comprises an iron circle 21a, which partially surrounds the magnetic coil 18a.
  • the iron circle 21a comprises in the region of the pump interior a magnetically insulating gap 22a which interrupts the iron circle 21a.
  • the iron circle 21a comprises a yoke element 35a, which surrounds the magnet coil 18a in particular on the outside, and two pole shoe elements 36a, 37a adjoining the yoke element 35a, between the ends of which the magnetically insulating gap 22a is arranged.
  • the piston 10a comprises an anchor element 12a, which consists entirely of a magnetizable material.
  • the armature element 12a In a rest position, i. at a pressure of 0 bar within the pump interior and with the solenoid 18a turned off, the armature element 12a has a position in which it partially overlaps axially with the gap 22a which the iron circuit 21a interrupts.
  • the magnet coil 18a When the magnet coil 18a is energized, a magnetic flux sets in the iron circle 21a and the armature element 12a, a magnetic resistance which counteracts this magnetic flux being determined, in particular, by a remaining gap width between the armature element 12a and the iron circle 21a. Since such a system tends to assume a state where the magnetic resistance is minimal, an actuating force acting on the armature member 12a acts to deflect the armature member 12a from its rest position against a force of the barrel 20a.
  • the magnetic coil 18a is energized with a pulse-shaped voltage, whereby adjusts a constantly changing magnetic field in the region of the pump interior.
  • the pulsed magnetic field in turn causes the piston 10a is first deflected with increasing strength of the magnetic field from its rest position against the force of the pump 20a. If the magnetic field is maximum, the piston 10a is also deflected to the maximum. As soon as a current through the magnet coil 18a is reduced, and thus the strength of the magnetic field drops again, the piston 10a is again moved in the direction of the rest position by the force of the pump 20a.
  • the magnetic coil 18a is preferably connected upstream of a diode unit, whereby the magnetic coil 18a only with a half-wave of a AC voltage is energized.
  • the solenoid 18a is provided for an AC voltage of 230 V at 50 Hz.
  • the piston 10a When the piston 10a is mounted, the pump interior forms an antechamber 23a and a compression chamber 24a.
  • the piston 10 a comprises a piston valve 25 a, which is fluidically arranged between the prechamber 23 a and the compression chamber 24 a.
  • the piston valve 25a is in the form of a check valve which has a passage direction from the prechamber 23a into the compression chamber 24a.
  • a filling stroke in which the piston 10a is moved by the magnetic field against the force of the pump 20a, fluid flows from the prechamber 23a through the piston valve 25a into the compression chamber 24a.
  • a subsequent pressure stroke In a subsequent pressure stroke in which the piston 10a is moved by the force of the pump 20a, the fluid is forced out of the compression chamber 24a.
  • the maximum pressure which acts on the fluid depends in particular on the force of the pump 20a.
  • a way by which the piston 10a is moved depends on a configuration of the oscillating piston pump. In one embodiment as a high pressure pump, the piston 10a is moved by about 10-11 mm. In one embodiment as a low-pressure pump, the piston 10a is moved by approximately 9-10 mm.
  • the piston 10a without the piston valve 25a is made in three parts in the illustrated embodiment.
  • the piston 10a which is provided for conveying the fluid, comprises a pressure piston element 11a and the armature element 12a, which is embodied separately from the pressure piston element 11a.
  • the piston 10 a comprises a sealing element 26 a, which has an outer sealing surface 27 a, which is provided for a fluid-tight connection with the piston guide 38 a.
  • the sealing surface 27a has an axial extension, which is adapted to a maximum possible deflection of the piston 10a relative to the piston guide 38a.
  • the armature element 12a and the pressure piston element 11a are firmly coupled with each other for one direction of force.
  • the anchor element 12a is designed in the form of a sleeve and is made entirely of the magnetizable material.
  • the plunger member 11a is entirely made of a non-magnetic material.
  • the magnetic field and thus the actuating force which can be adjusted by means of the magnetic coil 18 a, thus acts in particular on the armature element 12 a, which for the force direction, that of the.
  • the Corresponding magnetic field acting force is fixedly coupled to the pressure piston element 11 a.
  • the anchor element 12a is arranged completely in the prechamber 23a.
  • the piston guide 38a comprises a seal 28a against which the sealing surface 27a of the sealing element 26a of the piston 10a bears.
  • the pressure piston element 11a to which the armature element 12a and the sealing element 26a are connected, passes through a sealing plane, which is geometrically stretched by the seal 28a. In the rest position, the plunger member 11a is partially disposed in the compression chamber 24a and partially in the prechamber 23a.
  • the pressure piston element 11a protrudes in the rest position into the compression chamber 24a.
  • the magnet coil 18a When the magnet coil 18a is energized, the pressure piston element 11a is moved out of the rest position.
  • the piston 10a is again moved toward the rest position by the passages of the springs 20a, the pressure piston element 11a displaces the fluid from the compression chamber 24a.
  • the compression chamber 24a has an outlet with an outlet valve 29a, through which the fluid is forced out.
  • the anchor element 12a is in the form of a sleeve which almost completely encloses the pressure piston element 11a.
  • the anchor member 12a is formed as a bending member made by bending a semi-finished product.
  • a sheet metal is preferably used, which is bent in the form of the sleeve.
  • the anchor element 12a has, in the illustrated embodiment, a round cross-section. In principle, however, the anchor element 12a may also have an at least partially oval or at least partially angular cross section, such as a flattened cross section.
  • the anchor element 12a is formed as a sheet metal bent part, which is rolled in the form of the sleeve.
  • the anchor element 12a thereby has on one side a longitudinal slot 30a which is formed by side edges of the original sheet (cf. FIG. 2 ).
  • the side edges loosely border each other.
  • the longitudinal slot 30a has a width of almost zero, ie the anchor element 12a has a circumferential extent of almost 360 °.
  • the side edges can also be positively and / or materially connected to each other, whereby the anchor element 12a can be formed as a complete sleeve with a round cross section. to To reduce tolerances, the anchor element 12a can be ground centerless after forming.
  • the anchor element 12a is made of a corrosion-resistant steel.
  • the material used is an alloyed steel according to EN 1.4016 or EN 1.4113. Both are steel grades with a different chromium content. In particular, the chromium content of both types of steel have improved corrosion protection, with steel according to EN 1.4113 in this respect is assessed as superior quality than steel according to EN 1.4016.
  • Steel according to EN 1.4016 (X 6 Cr 17 ) has a chromium content of 16%.
  • Steel according to EN 1.4131 (X 6 CrMo 17 ) has a lower chromium content.
  • the anchor element 12a is therefore preferably made of steel according to EN 1.4131.
  • the anchor element 12a is attached to the pressure piston element 11a.
  • the anchor member 12a and the plunger member 11a are first fully formed, i. the anchor member 12a and the plunger member 11a are not further deformed during assembly.
  • armature element 12a is plugged onto the pressure piston element 11a, wherein a force which is necessary for plugging, is substantially smaller than the actuating force which can be exerted on the armature element 12a by means of the magnetic field coil.
  • the force which is necessary for plugging is in particular also smaller than the force exerted by the pump 20a in the basic position on the pressure piston element 11a.
  • the receptacle for the anchor element 12a may be subject to play.
  • the pressure piston element 11a forms a receptacle for the armature element 12a, which has a mounting direction directed along the direction of force, in which the armature element 12a is fixedly coupled to the pressure piston element 11a.
  • the Aufsteckides is thus directed along a direction in which the actuation force acts, which can be generated by means of the magnetic field coil.
  • the armature element 12a is thus stuck from one side onto the pressure piston element 11a, which in the assembled state faces the compression chamber 24a.
  • the pressure piston member 11a On the compression chamber 24a facing side, relative to the receptacle for the anchor member 12a, the pressure piston member 11a has a maximum outer diameter in all cross-sectional planes, which is smaller than an outer diameter, which has the recording.
  • the receptacle is provided essentially for the radial positioning of the anchor element 12a.
  • the anchor element 12a has an inner diameter that substantially corresponds to the outer diameter of the receptacle.
  • the receptacle receives the anchor element 12a without play. Tolerances in the manufacture of the anchor member 12a and the receptacle are aligned therewith that the anchor member 12a jammed on the receptacle. However, the clamping force is not so great that it is sufficient alone for supporting the actuating force and thus for fixing the armature element 12a on the pressure piston element 11a.
  • the pressure piston element 11a has an outer contour forming the receptacle of the armature element 12a with a surface which is non-deforming in the axial direction (cf. FIG. 4 ).
  • the armature element 12a has an inner contour provided for arrangement on the pressure piston element 11a, with a surface which is free of form-fitting in the axial direction (cf. FIG. 3 ).
  • the receptacle is thus provided only for non-positive connection with the anchor element 12a.
  • the receptacle itself, which radially positions the anchor element 12a does not serve for the axial fixation of the anchor element 12a.
  • the receptacle, on which the anchor element 12a is arranged is free in the axial direction, in particular, of undercuts or elevations which serve to fix the anchor element 12a.
  • the pressure piston element 11a has a stop 31a adjacent to the receptacle against which the armature element 12a rests in the assembled state.
  • the stop 31a is directly adjacent to the receptacle. Only the stop 31a provides a positive connection, which can absorb axial forces and thus the anchor member 12a and the plunger member 11a axially fixed to each other.
  • the stopper 31a limits a mounting depth for the anchor element 12a.
  • the stop 31a is formed in the form of a step which projects radially beyond the receptacle.
  • the anchor element 12a has an end face which in the assembled state rests positively against the stop 31a.
  • the pressure piston element 11a passes through the anchor element 12a completely. Basically that is Pressure piston element 11a subdivided into three sections. In this case, the first section which, on the side which faces the pre-chamber 23a, projects beyond the anchor element 12a, forms the stop 31a. The second section, in which the pressure piston element 11a passes through the anchor element 12, forms the receptacle.
  • the third section which projects beyond the anchor element 12a on the side facing the compression chamber 24a, is provided in particular for the arrangement of the sealing element 26a and for the displacement of the fluid from the compression chamber 24a.
  • the pump 20a is also supported.
  • the pressure piston element 11a is formed as a plastic part. As a plastic while a temperature-resistant thermoplastic is used.
  • the pressure piston element 11a can in principle be produced by means of a deep-drawing process. However, the pressure piston element 11a is preferably designed as an injection-molded component.
  • the pressure piston element 11a has a delivery channel 32a and a plurality of pressure equalization channels 15a, 16a, 17a.
  • the delivery passage 32a in which the spool valve 25a is arranged serves to connect the prechamber 23a to the compression chamber 24a.
  • the pre-chamber 23a has by the arrangement of the anchor member 12a on a front part and a rear part, which are connected in parallel by the pressure equalization channels 15a, 16a, 17a.
  • a housing stop 33a is provided for the piston 10a, which limits movement of the piston 10a.
  • the housing stopper 33a preferably has elastic elements for damping.
  • the delivery channel 32a is formed in the form of a bore which completely penetrates the pressure piston element 11a along its longitudinal axis.
  • the pressure compensation channels 15a, 16a, 17a are introduced in the form of grooves in the pressure piston element 11a.
  • the pressure compensation channels 15a, 16a, 17a are formed as depressions, which are introduced radially outward into the pressure piston element 11a.
  • the anchor element 12a delimits, in partial regions, the pressure compensation channels 15a, 16a, 17a, which are passed through the front end by the stop 31a for the anchor element 12a (cf. FIG.
  • the pressure equalization channels 15a, 16a, 17a terminate before the sealing plane of the seal 28a. Only the conveying channel 32a passes through the sealing plane.
  • the piston 10a on the sealing element 26a which is formed in the form of a sleeve and fixedly connected to the pressure piston element 11a.
  • the seal member 26a having the outer seal surface 27a is formed of metal.
  • the sealing surface 27a forms a sliding surface for the seal 28a.
  • the pressure piston element 11a has an undercut which is provided for engagement with the sealing element 26a.
  • the sealing element 26a is bent inwardly at its end facing the pre-chamber 23a and forms a clamp. In the assembled state, the clamp formed by the sealing element 26a engages in the undercut and connects the sealing element 26a and the pressure piston element 11a captive with each other.
  • the sealing element 26a is flanged around the pressure piston element 11a. In principle, however, it is also conceivable to form the sealing element 26a as a deep-drawn part with a corresponding configuration.
  • the piston valve 25a which is connected to the pressure piston element 11a, sealingly closes off with the sealing element 26a.
  • the pump 20a pushes the piston 10a against the housing stop 33a.
  • the armature element 12a is thereby axially fixed between the stop 31a formed by the pressure piston element 11a and the housing stop 33a.
  • the actuating force generated by means of the magnetic coil 18a engages the armature element 12a.
  • the anchor member 12a is thereby pressed against the stopper 31a, whereby it is axially fixed.
  • the fluid which is in the prechamber 23a is redistributed between the rear part and the front part of the prechamber 23a via the pressure equalizing passages 15a, 16a, 17a.
  • a resulting pressure difference acts at least partially on the armature element 12a and braces it against the stop 31a of the pressure piston element 11a.
  • the anchor element 12a is due to its Mass inertia with an acceleration of the piston 10 a during the pumping stroke against the stop 31 a pressed.
  • the anchor member 12a is positively connected to the plunger member 11a only along the operation force, an axial position of the anchor member 12a is always defined.
  • the oscillating armature pump is formed in the illustrated embodiment as a high-pressure pump for a household appliance.
  • the anchor element 12a has an inner diameter of 14 mm and an outer diameter of 20 mm.
  • the solenoid 18a has a coil diameter of 47 mm, i. a maximum diameter of the coil housing 19a surrounding the magnetic coil 18a is 47 mm.
  • the coil diameter is thus greater by a factor of 2.35 than the outer diameter of the anchor element 12a.
  • the armature element 12a and the magnet coil 18a of the oscillating armature pump have a different dimension.
  • the anchor element 12a then has an inner diameter of 9 mm and an outer diameter of 13 mm.
  • the sheet from which the anchor element 12a is formed thus has a thickness of 2 mm.
  • the magnet coil 18a has a coil diameter of 32.5 mm in such an embodiment. The coil diameter is then larger by a factor of 2.5 than the outer diameter of the armature element 12a, and thus smaller than 3.0.
  • FIG. 6 a further embodiment of the invention is shown.
  • the following descriptions are essentially limited to the differences between the embodiments, with respect to the same components, features and functions on the description of the embodiment of FIGS. 1 to 5 can be referenced.
  • the letter a in the reference numerals of the embodiment in the FIGS. 1 to 5 by the letter b in the reference numerals of the embodiment of FIG. 6 replaced.
  • With respect to identically designated components in particular with regard to components with the same reference numerals, can in principle also to the drawings and / or the description of the embodiment of FIGS. 1 to 5 to get expelled.
  • FIG. 6 shows a vibration pump with a solenoid coil 18b and a piston 10b, which is provided for conveying a fluid under the action of a back pressure.
  • the piston 10b has a pressure piston element 11b and an armature element 12b designed separately from the pressure piston element 11b.
  • the anchor element 12b is fixedly coupled to the pressure piston element 11b for one direction of force.
  • the anchor element 12b is designed in the form of a sleeve and consists of a magnetizable material. According to the preceding embodiment, the anchor member 12b is formed as a bending member.
  • the anchor element 12b is formed from a sheet metal, which is made in two parts.
  • the anchor member 12b has an inner plate member 13b and an outer plate member 14b.
  • the inner plate member 13b is disposed inside the outer plate member 14b.
  • the two sheet metal elements 13b, 14b are first firmly connected to each other, for example, by beads, which are introduced into the sheet metal elements 13b, 14b after they were placed on each other.
  • the sheet metal elements 13b, 14b can also be connected to one another in a material-locking manner.
  • the two interconnected sheet metal elements 13b, 14b then form the sheet, which is rolled to form it as the anchor element 12b in the form of a sleeve.
  • the inner plate member 13b and the outer plate member 14b have different axial lengths.
  • the inner plate member 13b and the outer plate member 14b terminate in the same plane.
  • the outer sheet metal element 14b is in the axial direction via the inner sheet metal element 13b over.
  • the anchor element 12b has two partial regions with different material thicknesses.
  • the two sheet metal elements 13b, 14b themselves have in the illustrated embodiment, a substantially equal material thickness.
  • the piston 10b is movable beyond a rest position due to its inertia.
  • the oscillating armature pump has, in addition to the pump 20b, a damping spring 34b, which counteracts the pumping of the piston 20b.
  • the one subregion in which the material thickness is greater is provided in particular for guiding the magnetic field of the magnetic coil 18b.
  • the other portion forms a receptacle for the damping spring 34b.
  • the side of the anchor element 12b, on which the two sheet metal elements 13b, 14b terminate in the same plane, serves for the positive connection with the pressure piston element 11b.
  • the side on which the outer plate member 14b protrudes beyond the inner plate member 13b forms the receptacle for the damping spring 34b.
  • the outer sheet metal element 13b surrounds the damping spring 34b, which is guided radially through the pressure piston element 11b.
  • the damper spring 34b is axially supported between the inner plate member 13b and a piston guide 38b fixedly connected to a coil case 19b of the vibration pump.
  • the outer sheet metal element 14b can project beyond the inner sheet metal element 13b.
  • a supernatant is preferably at most half as large as the material thickness of both sheet metal elements 13b, 14b together.
  • the supernatant is preferably about 1 mm.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Details Of Reciprocating Pumps (AREA)

Claims (13)

  1. Piston pour une pompe à armature oscillante pour un appareil ménager,
    prévu pour un convoyage d'un fluide sous l'impact d'une contre-pression,
    avec un élément piston de pression (11a ; 11b) et avec un élément d'armature (12a ; 12b) réalisé séparément de l'élément piston de pression (11a ; 11b), qui est fixement raccordé avec l'élément piston de pression (11a ; 11b) pour au moins une direction de force et qui se compose au moins partiellement d'un matériau magnétisable, où l'élément d'armature (12a ; 12b) est enfiché sur l'élément piston de pression (11a ; 11b),
    caractérisé en ce que l'élément piston de pression (11a, 11b) pénètre complètement l'élément d'armature (11a ; 11b).
  2. Piston selon la revendication 1,
    caractérisé en ce que l'élément piston de pression (11a ; 11b) réalise un récipient pour l'élément d'armature (12a ; 12b), comprenant une direction d'enfichage orientée le long de la direction de force.
  3. Piston selon la revendication 2,
    caractérisé en ce que le récipient est prévu au moins pour un positionnement radial de l'élément d'armature (12a ; 12b).
  4. Piston selon l'une quelconque des revendications 2 ou 3,
    caractérisé en ce que l'élément piston de pression (11a ; 11b) présente un contour extérieur formant le récipient pour recevoir l'élément d'armature (12a ; 12b) et/ou l'élément d'armature (12a ; 12b) présente un contour intérieur prévu pour être disposé sur l'élément piston de pression (11a ; 11b) avec une surface qui est dépourvue d'une liaison par forme en direction axiale.
  5. Piston selon l'une quelconque des revendications précédentes,
    caractérisé en ce que l'élément piston de pression (11a ; 11b) forme une butée (31a) pour l'élément d'armature (12a, 12b), qui est prévue pour un appui d'une force actionnant attaquant à l'élément d'armature (12a ; 12b).
  6. Piston selon la revendication 5,
    caractérisé en ce que la butée (31a) délimite une profondeur d'enfichage pour l'élément d'armature (12a ; 12b).
  7. Piston selon l'une quelconque des revendications 5 ou 6,
    caractérisé en ce que l'élément d'armature (12a ; 12b) présente un côté frontal attenant, via liaison en forme, à la butée (31a ; 31b) en état monté.
  8. Piston selon l'une quelconque des revendications précédentes,
    caractérisé en ce que l'élément piston de pression (11a ; 11b) est réalisé comme part synthétique.
  9. Piston selon l'une quelconque des revendications précédentes,
    caractérisé en ce que l'élément piston de pression (11a ; 11b) est réalisé comme composant moulé par injection.
  10. Piston selon l'une quelconque des revendications précédentes,
    caractérisé en ce que l'élément piston de pression (11a ; 11b) comporte au moins un canal à compensation de pression (15a, 16a, 17a).
  11. Piston selon l'une quelconque des revendications précédentes,
    caractérisé en ce que l'élément d'armature (12a ; 12b) est réalisé comme composant de pliage en tôle, qui est roulé en forme de cosse.
  12. Pompe à armature oscillante pour une machine de café avec un piston (10a ; 10b) selon l'une quelconque des revendications précédentes.
  13. Procédé pour l'assemblage d'un piston (10a ; 10b) pour une pompe à armature oscillante, ledit piston (10a ; 10b) étant prévu pour un convoyage d'un fluide sous l'impact d'une contre-pression, avec un élément piston de pression (11a ; 11b) et avec un élément d'armature (12a ; 12b) réalisé séparément de l'élément piston de pression (11a ; 11b), qui est fixement raccordé avec l'élément piston de pression (11a ; 11b) pour au moins une direction de force et qui se compose au moins partiellement d'un matériau magnétisable, où l'élément d'armature (12a ; 12b) est enfiché sur l'élément piston de pression (11a ; 11b), en raison de quoi l'élément piston de pression (11a ; 11b) pénètre complètement l'élément d'armature (12a ; 12b).
EP14728923.5A 2013-07-15 2014-06-04 Piston pour une pompe à armature oscillante Active EP3022442B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102013107482.0A DE102013107482A1 (de) 2013-07-15 2013-07-15 Kolben für eine Schwingankerpumpe
PCT/EP2014/061578 WO2015007428A1 (fr) 2013-07-15 2014-06-04 Piston pour pompe à armature oscillante

Publications (2)

Publication Number Publication Date
EP3022442A1 EP3022442A1 (fr) 2016-05-25
EP3022442B1 true EP3022442B1 (fr) 2019-10-02

Family

ID=50897596

Family Applications (1)

Application Number Title Priority Date Filing Date
EP14728923.5A Active EP3022442B1 (fr) 2013-07-15 2014-06-04 Piston pour une pompe à armature oscillante

Country Status (3)

Country Link
EP (1) EP3022442B1 (fr)
DE (1) DE102013107482A1 (fr)
WO (1) WO2015007428A1 (fr)

Family Cites Families (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE6606046U (de) * 1968-03-26 1970-07-30 Fritz Georg Elektromagnetische kolbenpumpe
US3947788A (en) * 1974-09-03 1976-03-30 Spencer C. Schantz Solenoid
US4749343A (en) * 1986-08-08 1988-06-07 Facet Enterprises, Inc. High pressure fluid pump
GB8709082D0 (en) * 1987-04-15 1987-05-20 Eaton Sa Monaco Electrical fluid pump
CS273485B1 (en) * 1988-10-20 1991-03-12 Stanislav Kucera Electromagnetic piston pump
DE3904448A1 (de) * 1989-02-15 1990-08-16 Bosch Gmbh Robert Magnetanker
IT246634Y1 (it) * 1999-04-09 2002-04-09 Ulka Srl Pistone composito per pompa a vibrazione
TWM263415U (en) * 2004-06-28 2005-05-01 Chwan Jhe Entpr Co Ltd Composite piston for electromagnetic inductive reciprocating pump
JP4662991B2 (ja) * 2004-08-30 2011-03-30 エルジー エレクトロニクス インコーポレイティド リニア圧縮機
CN102597517A (zh) * 2009-09-09 2012-07-18 租赁联盟哈拉德施罗特和西斯科股份公司 往复运动泵
EP2726738A1 (fr) 2011-07-01 2014-05-07 WIK Far East Ltd Pompe à piston alternatif à entraînement magnétique
DE202011050598U1 (de) * 2011-07-01 2012-10-09 Wik Far East Ltd. Flüssigkeitspumpe

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

Also Published As

Publication number Publication date
EP3022442A1 (fr) 2016-05-25
WO2015007428A1 (fr) 2015-01-22
DE102013107482A1 (de) 2015-01-15

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