EP2726738A1 - Pompe à piston alternatif à entraînement magnétique - Google Patents

Pompe à piston alternatif à entraînement magnétique

Info

Publication number
EP2726738A1
EP2726738A1 EP12733650.1A EP12733650A EP2726738A1 EP 2726738 A1 EP2726738 A1 EP 2726738A1 EP 12733650 A EP12733650 A EP 12733650A EP 2726738 A1 EP2726738 A1 EP 2726738A1
Authority
EP
European Patent Office
Prior art keywords
armature
piston
component
channel
pump according
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.)
Withdrawn
Application number
EP12733650.1A
Other languages
German (de)
English (en)
Inventor
Pierre Mayoraz
Gaëtan DAYER
Ludovic Dovat
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
WIK Far East Ltd
Original Assignee
WIK Far East Ltd
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 claimed from DE201120050598 external-priority patent/DE202011050598U1/de
Priority claimed from DE201120050599 external-priority patent/DE202011050599U1/de
Priority claimed from DE201120050601 external-priority patent/DE202011050601U1/de
Application filed by WIK Far East Ltd filed Critical WIK Far East Ltd
Publication of EP2726738A1 publication Critical patent/EP2726738A1/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B17/00—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
    • F04B17/03—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors
    • F04B17/04—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors using solenoids
    • 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
    • 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
    • F04B53/02—Packing the free space between cylinders and 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
    • F01M1/00—Pressure lubrication
    • F01M1/02—Pressure lubrication using lubricating pumps
    • F01M2001/0207—Pressure lubrication using lubricating pumps characterised by the type of pump
    • F01M2001/0223—Electromagnetic pumps
    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01F—MAGNETS; INDUCTANCES; TRANSFORMERS; SELECTION OF MATERIALS FOR THEIR MAGNETIC PROPERTIES
    • H01F7/00—Magnets
    • H01F7/06—Electromagnets; Actuators including electromagnets
    • H01F7/08—Electromagnets; Actuators including electromagnets with armatures
    • H01F7/10—Electromagnets; Actuators including electromagnets with armatures specially adapted for alternating current
    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01F—MAGNETS; INDUCTANCES; TRANSFORMERS; SELECTION OF MATERIALS FOR THEIR MAGNETIC PROPERTIES
    • H01F7/00—Magnets
    • H01F7/06—Electromagnets; Actuators including electromagnets
    • H01F7/08—Electromagnets; Actuators including electromagnets with armatures
    • H01F7/16—Rectilinearly-movable armatures
    • H01F7/1607—Armatures entering the winding

Definitions

  • the invention relates to a reciprocating pump with magnetic drive, comprising a barrel enclosing a pump cylinder with an output bore, an electric cylinder coil for periodically generating a magnetic field, a movable from the magnetic field of the solenoid in the longitudinal direction of the pump chamber armature with a dipping into the pump chamber and by the movement the armature piston reciprocating therein, wherein the piston-armature member having an axial inlet channel, which armature is located in an armature space enclosing anchor housing and a pressure compensation path between the piston side and the inlet side of the armature is provided.
  • Such electric fluid pumps which are also referred to as solenoid pumps due to their electromagnetic drive or due to the movement of their piston-armature component as oscillating piston pump, are used when smaller amounts of liquid are to be promoted and / or when built by a pump a certain pressure shall be.
  • Such liquid pumps are used in household appliances, such as coffee machines, irons or the like. When such a liquid pump is used in a coffee machine, it serves to convey water required for beverage preparation from a water tank to a continuous heating device and then to the brewing unit. If such liquid pumps are used in coffee machines which are suitable as a so-called fully automatic machine for brewing espresso, such pumps can provide the pressure required for an espresso preparation of about 10 bar or more with sufficient delivery rate. Another advantage of such liquid pumps is their small size.
  • Such a liquid pump is known, for example, from EP 1 818 538 B1 or EP 0 288 216 B1.
  • Such a liquid pump is constructed from a cylinder enclosing a pump space, into which a piston moves in a longitudinal axial direction.
  • the cylinder has an outlet bore that expels fluid delivered by the piston during pump operation.
  • the armature has ferromagnetic properties.
  • the armature housing is surrounded by an electrical coil, through which a periodic magnetic field is generated.
  • the armature is supported by means of a return spring formed as a compression spring at a bottom of the armature housing.
  • the return spring acts on the armature and thus on the piston plunging into the cylinder in such a way that the liquid introduced into the pumping space pushes it out of the outlet bore due to the force of the spring.
  • the magnetic field built up by the cylindrical coil serves to move the armature and thus the piston back against the force of the return spring, increasing the current volume of the pump chamber.
  • the cylindrical coil is designed to generate a periodic magnetic field with alternating voltage and typically comprises a diode with which a magnetic field is generated only over the length of a half-wave of a period.
  • the piston-armature component In order to allow water to flow into the pump chamber, the piston-armature component has a central through-channel. This is acted upon by a water supply, which opens into the armature housing enclosed by the armature housing.
  • the liquid pump has an inlet connection, on which, for example, a hose connected to a water tank is seated.
  • such a liquid pump has an inlet valve and an outlet valve. Both valves are designed as one-way valves.
  • the valve body of the inlet valve is in its closed position at a located on the projecting into the pump chamber of the cylinder end of the piston, annular valve seat.
  • the valve body of the exhaust valve is in its closed position at one of the outlet bore associated with the cylinder, annular valve seat.
  • a transverse bore is introduced in an integrally formed on the armature annular cylinder section, through which a Wegsamkeit is provided by the piston-side armature space to the inlet channel.
  • This annular cylinder section has a larger outer diameter than the piston and does not dip into the cylinder. It is necessary for the functionality of the pressure balance to be open in any position of the oscillating piston.
  • a piston for a solenoid pump which is designed as a composite piston.
  • the armature is made with its cylindrical extension and the transverse bore of a first material - a ferromagnetic material - while the piston can be a metal tube of a general type with or without seam.
  • this composite piston of the piston is welded to the integrally formed on the armature cylinder section.
  • liquid pumps of the aforementioned type are relatively small. Nevertheless, there is a desire to further simplify this, in particular to make more cost-effective and to reduce the size required, if possible.
  • the present invention seeks to further develop an aforementioned liquid pump in such a way that it can be designed as simple as possible building and thus inexpensive and with a smaller longitudinal axial extent.
  • a generic liquid pump mentioned above in which the pressure equalization has at least one opening in the piston side portion of the armature space channel, the piston side with the inlet side connecting longitudinal axis parallel to the swing axis of the piston-armature component and in the the piston-armature component is a composite component is, in which the anchor is a piece of pipe or is made of such, in the inner channel of the smaller diameter piston engages with a connecting portion and is connected to the armature.
  • the piston-armature component of this fluid pump has longitudinal axial travel to provide pressure balance capability between the piston side of the armature and the inlet side.
  • the inlet side may be the inlet channel section of the inlet channel assigned to the anchor. It is also possible that the pressure equalization in the form of one or more, the armature cross-channels is executed parallel to the longitudinal axis of the armature and thus opens at the inlet-side end side in the this side armature space section.
  • An advantage of this concept is not only the possible shorter design of the liquid pump but also that the pressure compensation path has a longitudinal extension which is parallel to the direction of movement of the piston-armature component.
  • an overflow of liquid from one armature side to the other armature side takes place optimized for flow, namely with the reduction of turbulence, which in turn results in a reduction of the overflow of the fluid from one armature space side to the other energy required.
  • the restoring compression spring needs to be equipped only with a correspondingly lower restoring force, which is why then the cylindrical coil unit can be made smaller.
  • the inlet channel within the anchor has a diameter which is greater than the Au OWmesser the piston and that the pressure balance is designed as one or more, the piston-side end face of the armature through cross-bore.
  • the at least one executed parallel to the longitudinal axis of the piston-armature component bore is arranged in a radial arrangement with respect to the outside of the piston that it opens into the inlet channel section of the armature. In the case of several holes, these are typically arranged at the same angular distance from each other, enclosing the piston.
  • the pressure balance for example in the form of multiple channels, passes through the armature in the longitudinal axial direction.
  • the channels are arranged at a distance from the outer lateral surface of the armature. It has been shown that then no loss of control of the armature by the magnetic field of the electric solenoid must be accepted.
  • piston-armature components which are designed as composite components in particular extent. This allows to form the armature through a pipe section, which makes at least as far as possible unnecessary machining of conventional piston-armature components. It also goes along with this concept that ultimately no or only little material waste arises.
  • one will provide the inner wall of the inlet channel section of the armature cylindrical, so that these need not be processed an additional processing step to produce certain geometries, since cylinder tubes typically have such a réellewandungsgeometrie in their manufacture.
  • the piston as another piece of pipe, typically made of another, especially cheaper material engages with a portion - a connecting portion - in the inner channel of the armature and is fixed therein, for which purpose preferably a clamping member is used.
  • a clamping member may be formed as a slotted polygonal tubular body, in the inner channel of the connecting portion of the piston is received and in turn is pressed into the inner channel of the armature and held therein by frictional engagement.
  • tubular tubular body not only to concentrate the clamping forces between the clamping member and the inner wall of the armature on the edges, but due to the geometry differences between the clamping member and the inner channel of the armature not filled by the clamping member cross-sectional areas of the round cross-section anchor channel at the same time the desired pressure equalization - opportunities. Likewise, pressure equalization paths are formed between the clamping member and the connecting portion of the piston.
  • Fig. 2a an end view of the piston-armature component of the figure
  • FIG. 3 is a longitudinal section through a piston-armature component in principle corresponding to that of Figure 2 in an alternative embodiment
  • FIG. 3a shows a perspective view of the piston-armature component of
  • FIG. 4 is a perspective view in the manner of an exploded view of the components of the reciprocating pump of Figure 1
  • End of the cylinder and armature housing formed component and 6 shows a perspective cross-sectional view of the pump housing of the liquid pump of FIGS. 1 and 2 as an insight into the inlet-side bottom of the pump housing.
  • a designed as a reciprocating pump with magnetic drive fluid pump 1, also address as a solenoid pump, has a cylinder 2, which encloses a pump chamber 3.
  • the pumping space 3 is limited on the output side by an outlet bore 4, which is introduced into the bottom 5 of the cylinder 2.
  • a connector socket 6 is formed, in which the output hole 4 opens. This has an internal thread for connecting a pressure line.
  • a piston 7 a From the inlet side engages in the pump chamber 3, a piston 7 a.
  • This is formed in the illustrated embodiment to an armature 8.
  • the consisting of piston 7 and armature 8 component is made of a ferromagnetic material in stainless steel quality.
  • This component passes through an inlet channel 9, with a first inlet channel section 10 being assigned to the anchor 8 and the adjoining inlet channel section 10. 1 to the piston 7.
  • the inner diameter of the channel portion 10 is greater than the outer diameter of the Zulaufkanalabitess 10.1 of the piston 7.
  • existing component in the piston-side end face 1 1 of the armature 8 are distributed circumferentially and arranged at equal angular distance from each other Introduced pressure equalization holes through which the piston side of the armature 8 with its upstream side - is connected to the inlet channel section 10.1. Due to the sectional view, only two of the three pressure compensation openings 12, 12.1 can be seen in FIG.
  • the piston-armature component shown in Figure 1 is not part of the invention and serves the principal description of the functionality thereof to produce a Druckausgangswegsamkeit between the piston side of the armature 8 and its inlet side.
  • the inlet side of the armature 8 is in this embodiment, the inlet channel section 10.1.
  • the longitudinal axes of the pressure compensation openings 12, 12.1 extend parallel to the axis of vibration of the component.
  • the openings 12, 12. 1 are arranged radially directly adjacent to the outer jacket surface of the piston 7.
  • the diameter of the inlet channel section 10. 1 is larger than the outside diameter. Diameter of the piston 7. Therefore, open the pressure equalization holes 12, 12.1 in parallel alignment in the inlet channel section 10.1.
  • the outer circumferential surface of the piston 7 is sealed to form a labyrinth seal against the inside of the cylinder 2. This is realized by a very narrow gap between these two longitudinally axially movable components. Thus, no additional seal is necessary between the outer wall of the piston 7 and the inner wall of the cylinder 2. This also means that the piston 7 runs easily during its oscillatory movement within the pump chamber 3.
  • the piston-armature component is guided in relation to its oscillating movement by the piston section engaging in the cylinder 2. Due to the above-described seal tumbling movements of the piston-armature component are avoided.
  • the armature 8 is located in an armature housing 13, which is formed in the illustrated embodiment of the cylinder 2.
  • armature housing 3 In the enclosed space of the armature housing 3 - the armature space - is on the inlet side, a compression spring 14 as a return spring, which is supported at one end to the armature 8 and at its other end to a bottom projection 15 of a pump housing 16.
  • the bottom projection 15 merges into a connecting piece 17 on the inlet side, onto which a supply hose (not shown) comes to rest.
  • the inlet hose is connected to a water supply.
  • the necessary movement gap between the outer surface of the armature 8 and the inside of the armature housing 13 can be very narrow dimensioned by a wobbling motion ,
  • a damping spring 18 is housed in the piston-side part of the armature space. This is held between an externally formed on the cylinder 2 flange 19 and the end face 1 1.
  • an electric cylinder coil unit On the armature housing 13, an electric cylinder coil unit is pushed.
  • the cylindrical coil unit is designed and designed so that a periodic magnetic field can be generated by this. Becomes a Magnetic field generated, is moved by this the armature 8 against the force of the compression spring 14 and thus the piston 7 pulled out by increasing the volume of the pump chamber from the cylinder 2. If the magnetic field is interrupted, the energy stored in the compression spring 14 presses the armature 8 and thus the piston 7 back into their position shown in FIG.
  • To generate the periodic magnetic field of the coil unit is associated with a diode and connected so that the magnetic field is generated only at one of the two AC voltage polarities. In this way, the piston-armature component oscillates in the longitudinal axial direction with respect to the longitudinal axis of the cylinder 2 and the armature space in the frequency of the AC voltage.
  • the piston 7 is equipped at its end projecting into the pumping space 3 with a spring-less one-way valve as the inlet valve 21. This opens when the piston 7 is moved in the direction of the inlet side. When the direction of movement is reversed in the direction of the bottom 5 of the cylinder 2, the valve 21 closes.
  • a second spring-less one-way valve is used as the outlet valve 22. Both valves 21, 22 are identical in the illustrated embodiment.
  • Such a valve without valve spring has a guide portion connected to its valve body, which is typically made in one piece with the valve body.
  • the guide section passes through the annular valve seat and protrudes in the case of the inlet valve into the inlet channel of the piston. In the case of the outlet valve, the guide section protrudes into the outlet bore of the cylinder enclosing the pump space.
  • the guide portion is in the inlet channel or the output hole respectively starting from the closed position of the valve in the axial direction to open the same movable and captive to the respective component - the piston or the cylinder - connected.
  • the longitudinal axial movability of the respective valve is dimensioned such that the opening cross-section is sufficient for passing the desired amount of water when lifted from the valve seat valve body.
  • valve seat-providing component - piston and / or cylinder - Such a conception, in which at least one of the two valves is connected to the valve seat-providing component - piston and / or cylinder - and thus allows proper functioning even without the use of valve springs, reduces the number of components required to form the valves considerably. Finally, in addition to the valve seat forming component basically only one other component, namely the valve is needed. In addition, there is no risk in this design that the functionality of the liquid pump can be affected by breakage of a valve spring.
  • a guide portion which is segmented in the circumferential direction.
  • the individual guide segment segments are spaced from each other, leaving flow gaps.
  • At least one of these guide segment segments carries a radially outwardly projecting Verklamm ceremoniessnase whose facing in the direction of the valve body surface constitutes a stop surface.
  • This abutment surface cooperates with a component-side abutment surface to limit the opening movement amount of the valve.
  • the component side abutment surface may be formed for example by a circumferential groove, as is preferred in the case of the inlet valve. This groove is introduced into the inner circumferential surface of the inlet channel of the piston.
  • the at least one clamping nose it is possible for the at least one clamping nose to engage behind the outlet bore and thus engage in the pump chamber.
  • a valve as prescribed can be inexpensively made of plastic, for example by means of a plastic injection molding process. If a use of plastic is not desired, it is advisable to produce the valve made of metal, for example a suitable brass alloy.
  • the valves 21, 22 can also be used independently of the concrete piston pump described concretely in the embodiment of FIG. 1 and also independently of the embodiment of the piston-armature component concretely described in the context of these embodiments.
  • FIG 2 shows a piston-armature component 23 according to the invention, which is designed as a composite component.
  • This piston-armature component 23 is part of a reciprocating pump with magnetic drive, as described for Figure 1.
  • the armature 24 is a piece of pipe made of a ferromagnetic material in stainless steel quality.
  • the armature 24 is cylindrical, as can be seen from the view of the component 23 in Figure 2a.
  • the anchor 24 can be made as a pipe section.
  • the piston 25 is also a metal pipe section.
  • the piston 25 is shown without the one-valve inlet valve associated therewith. Visible within the piston 25 in its immersed into the cylinder end portion in the inner wall introduced groove 26 in which the inlet valve is held clamped.
  • the piston 25 is connected with the interposition of a clamping member 27 with the armature 24, wherein the clamping member 27 and the piston 25 are inserted into the inner channel 28 of the armature and clamped therein.
  • the clamping member 27 in the illustrated embodiment is a slotted square tube piece (see FIG. 2a).
  • the clamping member 27 is for applying the desired clamping force slits.
  • the piston 25 is frictionally held in the clamping member with a connecting portion 29.
  • the polygonal design of the clamping member 27, wherein in the illustrated embodiment, a quadrangular (square) cross-sectional shape has been selected, serves the purpose that not the entire inner channel cross-sectional area is filled by the clamping member 27. In this way, four overflow 30 remain between the inner wall of the armature 24 and the outer side of the clamping member 27. Since the clamping member 27 of the illustrated embodiment extends through the anchor 24 in total, also the overflow 30 extend through the armature 24 therethrough. It is understood that for holding the piston 25, the clamping member 27 could have been designed shorter. In the illustrated embodiment, the clamping member 27 protrudes on both end sides of the armature 24 on this. These protruding portions serve to hold a return spring on the one hand and a damping spring on the other hand.
  • FIG. 3 shows a piston-armature component 23. 1, which is constructed in principle like the piston-armature component 23.
  • the piston-armature component 23. differs from the component 23 only in that the clamping member 27.1 on the piston side protrudes further from the armature 24.1.
  • the connecting portion 29.1 of the piston 25.1 ultimately does not penetrate into the interior of the armature 24.1.
  • the front view of the piston-armature component 23. 1 corresponds to that shown in FIG.
  • FIG. 3a shows the piston-armature component 23.1 in a perspective view.
  • FIG. 4 shows the individual building components of the liquid pump 1. It can be seen that the cylinder 2 and the armature housing 13 form a one-piece component. This component is identified by the reference numeral 23 in the figures.
  • the component 23 carries in the region of its inflow-side end portion a flange 31, which forms a contact flange for the assembly, generally designated by the reference numeral 32, which comprises the electrical components of the liquid pump 1.
  • FIG. 5 The enlarged perspective view of Figure 5 on the inflow-side end portion of the piston-armature component 23 makes the flange 31 clearly visible.
  • two bayonet cams 33, 33.1 projecting outward in the radial direction are provided as connecting members with which the component 23 can be detachably connected to the bottom 34 of the pump housing 16.
  • From the bayonet cams 33, 33.1 spaced from the inlet-side mouth of the component 23 is a circumferential groove 35 into which a sealing ring 36 is used to seal against the pump housing 16.
  • the base 34 of the pump housing 16 has an annular connecting recess 37, into which the connection-side connection section of the component 23 is inserted for connecting the component 23 to the pump housing 16.
  • FIG. 6 shows the connection recess 37, also with the cam bolts 31 complementary to the bayonet cams 33, 33.
  • the component 23 by inserting its connecting portion into the connecting recess 30 and corresponding rotation of the two components against each other this releasably sealed together connectable.
  • the sealing ring 36 acts against the inner wall of the connected components 16, 23. Bonding recess 37 (see Figure 1).
  • the provision of the pump housing 16 also allows the use of an electric solenoid, around which is not surrounded for insulation a plastic sheath. Therefore, in the pump housing 16 basically all necessary for the operation of the liquid pump 1 electrical / electronic components can be accommodated.
  • This also includes the fuse typically associated with such a fluid pump. Especially when such a fuse is designed as a thermal fuse, it can be arranged in the immediate vicinity of the coil and without an intermediate plastic layer. The modularity thus allows that when using a thermal fuse and after blowing through the same not the entire liquid pump, but only the assembly 25 or even only the fuse must be replaced.
  • connecting members can be arranged on the outside of the pump housing, in particular on its end face carrying the connecting piece 17, connecting members can be arranged. These can be used to connect one or more further units to the liquid pump 1. This may in particular be a flow measuring device in order to monitor the amount of liquid delivered by the liquid pump 1.
  • the links may be designed as a locking hook as part of a bayonet lock.

Landscapes

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

Abstract

L'invention concerne une pompe à piston alternatif à entraînement magnétique qui comporte un cylindre (2) contenant une chambre de pompe (3) et pourvu d'un orifice de sortie (4), une bobine électrique de cylindre pour générer périodiquement un champ magnétique, une armature (24, 24.1) déplaçable du champ magnétique de la bobine de cylindre dans la direction de l'axe longitudinal de la chambre de pompe (3) et comprenant un piston (25, 25.1) plongeant dans la chambre de pompe (3) et pouvant être amené à effectuer un va-et-vient par le déplacement de l'armature (24, 24.1). L'élément piston-armature (23, 23.1) présente un canal d'amenée axial (9), l'armature (24, 24.1) se trouvant dans un logement (13) d'armature contenant une chambre d'armature. Il est prévu un espace d'équilibrage de la pression entre le côté piston et le côté amenée de l'armature. Le espace d'équilibrage de la pression présente au moins un canal (30) qui débouche dans la partie du côté piston de la chambre d'armature et dont l'axe longitudinal reliant le côté piston au côté amenée s'étend parallèlement à l'axe d'oscillation de l'élément piston-armature (23, 23.1). L'élément piston-armature (23, 23.1) est un élément composite dans lequel l'armature (24, 24.1) est un élément tubulaire ou est fabriqué comme tel et dans le canal intérieur duquel le piston (25, 25.1) au diamètre plus petit s'engage avec une partie de liaison (29, 29.1) et est relié à l'armature (24, 24.1).
EP12733650.1A 2011-07-01 2012-06-29 Pompe à piston alternatif à entraînement magnétique Withdrawn EP2726738A1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE201120050598 DE202011050598U1 (de) 2011-07-01 2011-07-01 Flüssigkeitspumpe
DE201120050599 DE202011050599U1 (de) 2011-07-01 2011-07-01 Flüssigkeitspumpe
DE201120050601 DE202011050601U1 (de) 2011-07-01 2011-07-01 Flüssigkeitspumpe
PCT/EP2012/062712 WO2013004620A1 (fr) 2011-07-01 2012-06-29 Pompe à piston alternatif à entraînement magnétique

Publications (1)

Publication Number Publication Date
EP2726738A1 true EP2726738A1 (fr) 2014-05-07

Family

ID=46506338

Family Applications (1)

Application Number Title Priority Date Filing Date
EP12733650.1A Withdrawn EP2726738A1 (fr) 2011-07-01 2012-06-29 Pompe à piston alternatif à entraînement magnétique

Country Status (3)

Country Link
EP (1) EP2726738A1 (fr)
CN (1) CN103649535A (fr)
WO (1) WO2013004620A1 (fr)

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DE102013107482A1 (de) 2013-07-15 2015-01-15 Sysko AG Systeme und Komponenten Kolben für eine Schwingankerpumpe
DE102013107481A1 (de) 2013-07-15 2015-01-15 Sysko AG Systeme und Komponenten Kolben für eine Schwingankerpumpe
EP2873857B1 (fr) * 2013-11-15 2020-08-19 ODE (Hk) Company Limited Pompe à fluides
IT201800003064A1 (it) * 2018-02-27 2019-08-27 Elbi Int Spa Pompa a vibrazione con struttura migliorata.
CN114235320A (zh) * 2021-12-21 2022-03-25 中国科学技术大学 一种交流电磁铁式振动加载装置及方法
DE102022116095A1 (de) * 2022-06-28 2023-12-28 Sysko AG Systeme & Komponenten Treiberspulenvorrichtung

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CN103649535A (zh) 2014-03-19

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