EP3759349A1 - Pompe à vibrations à actionnement amélioré - Google Patents

Pompe à vibrations à actionnement amélioré

Info

Publication number
EP3759349A1
EP3759349A1 EP19711717.9A EP19711717A EP3759349A1 EP 3759349 A1 EP3759349 A1 EP 3759349A1 EP 19711717 A EP19711717 A EP 19711717A EP 3759349 A1 EP3759349 A1 EP 3759349A1
Authority
EP
European Patent Office
Prior art keywords
pump according
piston
hollow body
tubular portion
pump
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP19711717.9A
Other languages
German (de)
English (en)
Other versions
EP3759349B1 (fr
Inventor
Gabriele BELLATO
Paolo Da Pont
Giuseppe Marone
Alessandro Rovera
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.)
Elbi International SpA
Original Assignee
Elbi International SpA
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
Application filed by Elbi International SpA filed Critical Elbi International SpA
Publication of EP3759349A1 publication Critical patent/EP3759349A1/fr
Application granted granted Critical
Publication of EP3759349B1 publication Critical patent/EP3759349B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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
    • 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
    • F04B53/125—Reciprocating valves
    • F04B53/126—Ball valves
    • 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
    • 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
    • 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
    • F04B2203/00—Motor parameters
    • F04B2203/04—Motor parameters of linear electric motors
    • F04B2203/0403—Magnetic flux
    • 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
    • F04B2203/00—Motor parameters
    • F04B2203/04—Motor parameters of linear electric motors
    • F04B2203/0407—Force
    • 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
    • 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
    • F04B53/16—Casings; Cylinders; Cylinder liners or heads; Fluid 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
    • 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
    • F04B53/16—Casings; Cylinders; Cylinder liners or heads; Fluid connections
    • F04B53/162—Adaptations of cylinders
    • F04B53/164—Stoffing boxes

Definitions

  • the present invention relates to a vibration pump with improved actuation, in particular for a household appliance.
  • Vibration pumps are known, in particular for use in household appliances.
  • Such pump type generally comprises a hollow body having an inlet and an outlet, between which a fluid can flow.
  • the hollow body further comprises a work chamber located between the inlet and the outlet.
  • a piston at least partly made of ferromagnetic material and configured for sliding in the hollow body within the work chamber, so as to push the fluid from the inlet to the outlet.
  • a generator device configured for generating a magnetic field capable of commanding the displacement of the piston within the work chamber, and an elastic assembly situated within the work chamber and co operating with the piston.
  • the elastic assembly includes a pair of elastic members, in particular coil springs, both of which abut on axially opposite faces of the piston.
  • a first coil spring exerting a greater elastic force to withdraw the piston in one direction of movement against the action of the generator device
  • a second coil spring exerting a smaller elastic force to move the piston in an opposite direction of movement, so as to cause the piston to return into an initial position.
  • the elastic assembly comprises an elastic member connected to the piston.
  • the elastic member is configured for acting bidirectionally upon the piston during the displacement thereof in said work chamber.
  • the pump can operate in a reliable manner, allowing for effective control of the elastic force acting upon the piston by means of the bidirectional co-operation existing between the elastic member and the piston, permitted by the constraint effected through the connection between said elastic member and said piston .
  • Figure 1 is a longitudinal sectional view of a vibration pump made in accordance with an exemplary embodiment of the present invention.
  • Figure 2 is a partial longitudinal sectional view showing a piston of a vibration pump made in accordance with an exemplary embodiment of the present invention.
  • Figure 3 is a schematic graph representing the elastic force - displacement diagram of a piston of a vibration pump made in accordance with a further exemplary embodiment of the present invention.
  • Figure 4 is a partial longitudinal sectional view wherein a comparison is made between the operating positions taken by a piston of a vibration pump made in accordance with a further exemplary embodiment of the present invention, according to the graph shown in Figure 3.
  • Figure 5 is a perspective view of a pump made in accordance with another exemplary embodiment of the present invention .
  • Figure 6 is an axial or longitudinal sectional view of the pump of Figure 5.
  • numeral 1 designates as a whole a vibration pump made in accordance with an exemplary embodiment of the present invention.
  • said pump substantially extends along a longitudinal axis x-x. Therefore, the terms “axial”, “longitudinal”, “transversal” and “radial” as used in the following description should be considered to refer to said longitudinal axis x-x.
  • said pump 1 can be used for pushing a fluid, in particular a liquid, e.g. water, in machines for making beverages, such as coffee, tea or the like. More in general, pump 1 can be used in household appliances .
  • a fluid in particular a liquid, e.g. water
  • pump 1 can be used in household appliances .
  • pump 1 comprises a hollow body 6 having an inlet 8 and an outlet 10. Between inlet 8 and outlet 10 a fluid, in particular a liquid, e.g. water, can flow. Hollow body 6 comprises also a work chamber 7 located between inlet 8 and outlet 9.
  • a fluid in particular a liquid, e.g. water
  • Pump 1 further comprises a piston 2 at least partly made of ferromagnetic material and configured for sliding in the hollow body within work chamber 7, so as to push the fluid from said inlet 8 towards outlet 10.
  • pump 1 comprises a generator device, in particular a solenoid 4, configured for generating a magnetic field capable of commanding the displacement of piston 2 within work chamber 7.
  • pump 1 comprises an elastic member, particularly a spring 11 (e.g. a coil spring) co-operating with piston 2.
  • Said elastic member which in the illustrated embodiment comprises spring 11, is connected to piston 2 and is configured for acting bidirectionally upon piston 2 during the displacement thereof in work chamber 7.
  • spring 11 is mounted differently than in the embodiment shown in Figure 1; however, as will be apparent to a person skilled in the art, in the embodiment shown in Figure 4 it would be possible to adopt the same mounting arrangement of spring 11 as shown in Figure 1.
  • piston 2 moves from an initial or idle position PO (corresponding to a null elastic force acting upon piston 2) to a first operating position PI (corresponding to the maximum elastic force acting upon piston 2), with a displacement si.
  • piston 2 is pushed, under the withdrawing action of spring 11, from the first operating position PI to a second operating position P2 (corresponding to a negative elastic force acting upon piston 2) beyond initial or idle position PO .
  • the displacement of piston 2 is designated as s2.
  • piston 2 when piston 2 is in the second operating position P2, it is pulled (as opposed to pushed) by spring 11 towards final position P3 corresponding to initial or idle position PO .
  • the displacement of piston 2 is designated as s3.
  • spring 11 is connected to the piston at an axial end 11a thereof.
  • spring 11 is configured for working in both sliding directions of piston 2, and can therefore act upon piston 2 both by traction and by compression .
  • connection between the elastic member and piston 2 can be effected in different ways.
  • spring 11 and piston 2 are connected by mechanical coupling.
  • spring 11 and piston 2 are connected by welding.
  • spring 11 on the side opposite to that whereon it is connected to piston 2, is locked relative to hollow body 6.
  • pump 11 comprises a locking element 26 mounted on hollow body 16, wherein spring 11 is retained axially between locking element 26 and hollow body 6.
  • locking element 26 defines an annular housing 26a in which the other axial end lib of spring 11 is inserted, which is opposite to axial end 11a connected to piston 2.
  • locking element 26 comprises a centering portion 26b situated in a position radially internal to annular housing 26a and surrounded by spring 11.
  • spring 11 is thus retained, at its axial end lib, by hollow body 6 and, at its opposite axial end 11a, by piston 2 to which it is connected.
  • spring 11 is compression-loaded and tends to move piston 2 away from inlet 8 towards outlet 10, contrary to the magnetic action that solenoid 4 is configured to exert on piston 2.
  • piston 2 also has a through cavity 2a adapted to be selectively crossed by the fluid, through co-operation with a normally closed valve device 12 that can be opened by the pressure of the fluid in work chamber 7, so as to allow the fluid to flow from inlet 8 towards outlet 10.
  • piston 2 With reference to the embodiment shown by way of example in Figure 1, the following will describe in detail the structure of piston 2 and that of work chamber 7 in which piston 2 is slidably mounted.
  • piston 2 divides work chamber 7 into:
  • suction compartment 36 situated upstream of piston 2 and operationally intended to receive the fluid coming from inlet 8;
  • compensation compartment 38 communicating with suction compartment 36 and fluidically separate from delivery compartment 9, so as to allow the reciprocating motion of piston 2.
  • Communication between suction compartment 36 and compensation compartment 38 may occur through a communication duct formed between them.
  • said communication duct may be obtained by means of one or more recesses formed along the radially internal lateral surface of hollow body 6 and/or along the radially external lateral surface of piston 2.
  • piston 2 comprises a radially external annular portion 17 and a radially internal tubular portion 16 protruding axially from annular portion 17.
  • Tubular portion 16 internally defines through cavity 2a.
  • annular portion 17 and tubular portion 16 are made as two separate components, which are then mutually connected during assembly to form a single piston.
  • annular portion 17 and tubular portion 16 are both made of steel, in particular each one of them being made of a different steel type; as an alternative, tubular portion 16 may also be made of plastic material (e.g. by injection moulding) .
  • tubular portion 16 may be made of steel.
  • tubular portion 16 may be manufactured by extrusion.
  • extrusion process avoids the use of numerical control machines, e.g. a lathe, for manufacturing tubular portion 16.
  • This aspect is advantageous because such a process generates, on the outer surface of the tubular portion, machining lines oriented substantially in the longitudinal direction, which, for this very reason, do not substantially affect the life of the annular gasket (e.g. an 0-ring) .
  • machining by machine tool i.e. by removal of material, as in a lathe
  • transversal machining lines that cause significant wear of said annular gasket 19 during the use of the pump.
  • annular portion 17 and tubular portion 16 are slidably supported by hollow body 6 within work chamber 7.
  • annular portion 17 is slidably supported between suction compartment 36 and compensation compartment 38, thus creating a mobile division between them.
  • tubular portion 16 is slidably supported in delivery compartment 9.
  • suction compartment 36 and compensation compartment 38 have substantially the same cross-section.
  • tubular portion 16 is inserted into annular portion 17 and crosses it in the axial direction. Also, tubular portion 16 comprises a protruding tract 16a that extends axially beyond annular portion 17.
  • protruding tract 16a is slidably supported by delivery compartment 9.
  • delivery compartment 9 has a smaller cross-section than that of the rest of work chamber 7, i.e. that of suction compartment 36 and of compensation compartment 38.
  • protruding tract 16a of tubular portion 16 is slidably and sealingly housed in delivery compartment 9.
  • the example shows an annular gasket 19 situated in delivery compartment 9 and operationally arranged around protruding tract 16a.
  • pump 1 comprises a retaining bushing 21 that retains annular gasket 19 axially in abutment against a seat formed in hollow body 6.
  • retaining bushing 21 is coupled to hollow body 6, in particular by ultrasonic welding in an annular housing of the hollow body, located upstream of annular gasket 19.
  • retaining bushing 21 may be connected to the hollow body by mechanical coupling, e.g. by interference fit.
  • retaining bushing 20 consists of a teflon disk having an axial through cavity.
  • tubular portion 16 has no apertures in its side walls, but the fluid flowing through tubular portion 16 is intended to exit only through the axial end of protruding tract 16a.
  • tubular portion 16 has a flange 16b in an opposite position of protruding tract 16a.
  • head portion or flange 16b is axially in abutment against annular portion 17.
  • spring 11 is retained axially between tubular portion 16 and annular portion 17.
  • end 11a of spring 11 is retained between flange 16b and axial end 17a of annular portion 17. This provides an exemplary mechanical coupling between spring 11 and piston 2.
  • spring 11 may be coupled or secured to piston 2 in a different manner.
  • said spring 11 may be directly coupled to annular portion 17, without it being axially retained between said annular portion 17 and tubular portion 16.
  • tubular portion 16 may even lack flange 16b, being however still coupled to annular portion 17.
  • tubular portion 16 when piston 2 is mounted, tubular portion 16, after having been inserted into annular portion 17, is locked on annular portion 17.
  • locking occurs by plastic deformation of protruding tract 16a against the walls of annular portion 17, e.g. by caulking and/or squashing.
  • tubular portion 16 - in this case preferably made of plastic material - is connected to annular portion 17 by interference fit.
  • tubular portion 16 comprises a plurality of lateral fins 16c, preferably having an inclined profile, situated in an intermediate tract and tending to expand elastically outwards in a radial direction.
  • lateral fins 16c When tubular portion 16 is inserted into annular portion 17 and lateral fins 16c enter annular portion 17, they are pushed in such a way that they will withdraw radially inwards (in particular, due to co-operation between the inclined profile and the shoulder of annular portion 17) .
  • lateral fins 16c are again free to expand radially outwards. Should tubular portion 16 be then pushed backwards, lateral fins 16c are configured to abut axially against annular portion 17 and prevent extraction or removal of the tubular portion from annular portion 17.
  • spring 11 is housed in suction compartment 36 and operates by compression to withdraw piston 2 from the first operating position Pi (into which it is attracted by the magnetic force generated by solenoid 4 ) .
  • spring 11 may be situated in compensation compartment 38 and be still connected to piston 2 (to the face thereof located in compensation compartment 38) .
  • spring 11 is arranged to work by traction, so as to be capable of withdrawing piston 2, in particular from the first operating position Pi (into which it is attracted by the magnetic force generated by solenoid 4) .
  • spring 11 is connected to piston 2 (and possibly also to hollow body 6) .
  • Such connection may be effected by welding and/or mechanical coupling .
  • valve device 12 housed in piston 2 and the principle of operation thereof.
  • Valve device 12 is normally closed and can be opened by the fluid in suction device 36, under the action of the reciprocating motion of piston 2.
  • valve device 12 when solenoid 4 is electrically de energized, spring 11 pushes piston 2 back towards outlet 10, thereby increasing the volume of suction compartment 36 and reducing the pressure acting upon the fluid contained therein. In this way, valve device 12 returns into the closed position, thus stopping the flow of fluid through through cavity 2a.
  • valve device 12 includes a mobile shutter 12a within through cavity 2a, a seat 12b formed in through cavity 2a, and an elastic element, e.g. a return spring 18, acting upon mobile shutter 12a and tending to hold it against seat 12b.
  • seat 12b is formed in an axially intermediate position of through cavity 2a, which, in the illustrated embodiment, is defined in tubular portion 16.
  • mobile shutter 12a comprises a ball shutter .
  • seat 12b consists of a narrower portion defined in an intermediate portion of through cavity 2a.
  • said narrower portion is defined by tubular portion 16, e.g. by a radially inward deformation of the latter .
  • return spring 18 is housed in through cavity 2a and is connected to one end of piston 2. Return spring 18 acts upon mobile shutter 12a to hold it against seat 12b.
  • return spring 18 is connected to the downstream end of piston 2 and, being compression preloaded, presses against mobile shutter 12a.
  • pump 1 comprises a non-return valve 14 situated in hollow body 6 downstream of work chamber 7, in particular of delivery compartment 9, and upstream of outlet 10.
  • Said non-return valve 14, including a respective spring 15, is designed to prevent the fluid from returning from outlet 10 towards work chamber 7, in particular towards delivery compartment 9.
  • Solenoid 4 is in a position radially external to piston
  • pump 1 comprises a ferromagnetic assembly arranged around hollow body 6 and comprising, at least partly, ferromagnetic material.
  • the ferromagnetic assembly is positioned transversally between solenoid 4 and hollow body 6.
  • said ferromagnetic assembly comprises a pair of blocks 5 of ferromagnetic material interposed between solenoid 4 and hollow body 6 in which piston 2 slides.
  • Such blocks 5 preferably have a "C" shape.
  • Each block 5 is arranged circumferentially around core 2.
  • Solenoid 4 is conveniently housed in a respective housing 40 mounted around hollow body 6.
  • tubular portion 16 and annular portion 17 are simple and economical to implement.
  • tubular portion 16 is configured in a manner such that the fluid will flow from suction compartment 36 to delivery compartment 9 through cavity 2a. Therefore, the fluid cannot flow from compensation compartment 38 to delivery compartment 9 through the side walls of tubular portions 16.
  • tubular portion 16 have no such apertures as to allow the fluid to flow directly from compensation compartment 38 to the inside of tubular portion 16 and then back into suction compartment 36.
  • pump 1 further comprises an integrated flow-rate measuring device.
  • Such device is intended to measure the flow rate of the fluid being delivered by the pump.
  • the flow-rate measuring device is situated upstream of piston 2, in particular upstream of work chamber 7, with reference to the fluid flow.
  • the flow-rate measuring device comprises:
  • impeller 20 situated between piston 2 and inlet 8, and configured for being turned by a flow of fluid entering through inlet 8 and directed towards work chamber 7, and
  • sensing device 24 configured for sensing the rotation of impeller 20, for the purpose of measuring the fluid flow rate .
  • sensing device 24 comprises a magnetic sensor.
  • impeller 20 comprises one or more magnets 22, and sensing device 24 is adapted to sense the rotation of magnet 22 for the purpose of measuring the fluid flow rate.
  • Sensing device 24 is configured for sensing magnetic field variations caused by the rotation of impeller 20 and of magnet 22 integral with said impeller 20.
  • sensing device 24 may be a sensor of the electric, electronic or magnetic type, such as, for example, a magnetic sensor.
  • Impeller 20 is adapted to turn about an axis of rotation x- x, which, in particular, is coaxial to piston 2. Impeller 20 is conveniently supported in rotation by a support.
  • said impeller support is, advantageously, the previously mentioned locking element 26.
  • said support may be a separate component .
  • the support which in the illustrated embodiment is provided by locking element 2, has a pin 28 inserted into a matching recess in impeller 20, so as to allow rotation thereof.
  • the pump is very compact, and there is no need for a long tube connecting outlet 10 or inlet 8 to an external flowmeter, in which the liquid, e.g. water, may stagnate.
  • This aspect is particularly advantageous in beverage dispensers, wherein it is advantageous to prevent the liquid from remaining in contact with the outside environment for long periods of time; also, this prevents undesired dripping.
  • sensing device 24 is of the optical type, e.g. for reading reading portions (e.g. differently coloured stripes or other distinctive marks) on impeller 20.
  • pump 1 includes a cover 32 removably mounted (e.g. by means of screws 33) to hollow body 6, between which a gasket 34 is conveniently interposed.
  • cover 32 housing chamber 30 is formed. Housing chamber 30 is defined between cover 32 and hollow body 6.
  • cover 32 comprises inlet 8.
  • the sensing device is associated with cover 32.
  • inlet 8 is configured to direct a flow of fluid tangentially onto impeller 20, particularly onto blades of impeller 20.
  • the pump is comprised in an apparatus, such as a beverage dispensing machine or a coffee-making machine, and, when said apparatus is resting on a horizontal surface, hollow body 6, and in particular work chamber 7, is tilted relative to a horizontal plane, e.g. by an angle of 10° to 80°, preferably 10° to 60°, more preferably 10° to 30°.
  • an angle of 10° to 80° preferably 10° to 60°, more preferably 10° to 30°.
  • work chamber 7 as a whole is situated in a higher position than impeller 20 or housing chamber 30.
  • the tilted position corresponds to the position taken by the pump of Figure 1 when it is turned counterclockwise by a few degrees.
  • impeller 20 can rotate while staying immersed in the liquid.
  • Cylinder 6, and in particular work chamber 7, is arranged on a longitudinal axis, which in particular coincides with axis x-x. Therefore, axis x-x can be tilted relative to the horizontal.
  • locking element 26 is movably and adjustably mounted in hollow body 6 in abutment against spring 11. This permits calibrating the compression exerted on piston 2 by elastic member 11 in a customized manner dependent on the specific operating conditions in which the pump will have to work.
  • locking element 26 is mounted in hollow body 6, and these are threadedly coupled together .
  • locking element 26 is at least partly made of ferromagnetic material.
  • annular portion 17 of core 2 has a substantially circular cross-section. More preferably, the inner cavity of annular portion 17 of core 2 also has a substantially circular cross-section.
  • pump 1 comprises also a connection element coupled around hollow body 6 and configured to allow the pump to be installed in a household appliance.
  • the connection element is a yoke 42 having a pair of lateral jaws or appendices 44 which seize hollow body 6 and which extend transversally beyond the latter, so as to allow the pump to be installed in a household appliance .
  • yoke 42 is in axial abutment against the assembly of ferromagnetic material, which preferably includes blocks 5, and retains it within hollow body 6.
  • yoke 42 is axially retained between solenoid 4 and a stopping member mounted on hollow body 6.
  • the stopping member is a hydraulic connector or union 46 mounted to one end, e.g. the outlet end, of hollow body 6.
  • yoke 42 is made of elastomeric material.
  • the ferromagnetic assembly further comprises a spacer 48 located between two blocks 5.
  • blocks 5 and spacer 48 are stackable in the axial direction and axially retained within hollow body 6 by the connection element, in particular yoke 42.
  • the ferromagnetic assembly is in axial abutment with a flange or perimetrical extension 50 of hollow body 6.
  • said ferromagnetic assembly is in axial abutment with the connection element, in particular yoke 42.
  • the pump illustrated in Figures 5 and 6 may not employ an elastic member, such as spring 11, connected to piston 2 and configured for acting bidirectionally upon piston 2 during the displacement thereof in work chamber 7.
  • said pump may be modified in such a way as to incorporate a pair of springs acting upon piston 2, as in the above- mentioned prior-art examples.
  • solenoid 4 shown in the illustrated embodiment may be replaced with any other generator device capable of creating a magnetic field.
  • spring 11 shown in the illustrated embodiment may be replaced with any other elastic member.
  • counter-spring 18 shown in the illustrated embodiment may be replaced with any other elastic member.
  • seat 12b is formed in an intermediate portion of piston 2.
  • intermediate position does not mean that said seat 12b should be equidistant from the axial ends of piston 2, but rather that said seat is in a position generally spaced out from both axial ends of the piston.
  • piston 2 comprises a tubular portion 16 and an annular portion 17 crossed by tubular portion 16.
  • the piston may also be constructed differently. For example, one may conceive a structure made up of two pieces assembled together, wherein the tubular portion is situated at the end of the annular portion without going through it as shown in Figures 1 to 4.
  • element 16 can have a small diameter, e.g. as small as 3 mm, and a thin tube, e.g. as thin as 0.2 mm. In other words, manufacturing element 16 requires less material.

Abstract

L'invention concerne une pompe qui comprend un corps creux (6) ayant une entrée (8) et une sortie (10) entre lesquelles un fluide peut s'écouler. Le corps creux (6) comprend en outre une chambre de travail (7) située entre l'entrée (8) et la sortie (10). Un piston (2) est constitué au moins partiellement d'un matériau ferromagnétique et est conçu pour coulisser dans le corps creux (6) à l'intérieur de la chambre de travail (7) de façon à pousser le fluide de l'entrée (8) vers la sortie (10). Un dispositif générateur (4) est conçu pour générer un champ magnétique capable de commander le déplacement du piston (2) à l'intérieur de la chambre de travail (7). Un élément élastique (11) coopère avec le piston (2). L'élément élastique (11) est raccordé au piston (2) et est conçu pour agir de manière bidirectionnelle sur le piston (2) pendant son déplacement dans la chambre de travail (7).
EP19711717.9A 2018-02-27 2019-02-27 Pompe à vibrations à actionnement amélioré Active EP3759349B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
IT102018000003069A IT201800003069A1 (it) 2018-02-27 2018-02-27 Pompa a vibrazione con attuazione migliorata
PCT/IB2019/051557 WO2019166956A1 (fr) 2018-02-27 2019-02-27 Pompe à vibrations à actionnement amélioré

Publications (2)

Publication Number Publication Date
EP3759349A1 true EP3759349A1 (fr) 2021-01-06
EP3759349B1 EP3759349B1 (fr) 2022-11-02

Family

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Family Applications (1)

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EP19711717.9A Active EP3759349B1 (fr) 2018-02-27 2019-02-27 Pompe à vibrations à actionnement amélioré

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IT201900025225A1 (it) * 2019-12-23 2021-06-23 A R S Elettromeccanica Srl Pistone mobile per pompe a vibrazione
IT202100007772A1 (it) 2021-03-30 2022-09-30 Elbi Int Spa Sistema di controllo per una pompa, in particolare per un apparecchio elettrodomestico.
IT202100007790A1 (it) 2021-03-30 2022-09-30 Elbi Int Spa Dispositivo di rilevazione per un flusso di liquido in un apparecchio elettrodomestico.

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US3136257A (en) * 1961-10-26 1964-06-09 Gorman Rupp Ind Inc Oscillating pump impeller
JPS6026185A (ja) * 1983-07-21 1985-02-09 Mitsubishi Electric Corp 往復動形流体機械
JPH08210248A (ja) * 1994-10-31 1996-08-20 Harry Ono 複式ピストン・ポンプ
IT246634Y1 (it) * 1999-04-09 2002-04-09 Ulka Srl Pistone composito per pompa a vibrazione
IL142779A0 (en) * 2001-04-24 2002-03-10 Mnde Technologies L L C Electromagnetic device particularly useful as a vibrator for a fluid pump
US7078832B2 (en) * 2002-10-16 2006-07-18 Matsushita Refrigeration Company Linear motor, and linear compressor using the same
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
DE102014113508A1 (de) * 2014-09-18 2016-03-24 Sysko Ag Schwingankerpumpe
DE102015107207A1 (de) * 2015-05-08 2016-11-10 Pierburg Gmbh Magnetpumpe für ein Hilfsaggregat eines Fahrzeugs

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WO2019166956A1 (fr) 2019-09-06
IT201800003069A1 (it) 2019-08-27

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