EP2519744B1 - Pompe ayant une valve avec un dispositif d'amortissement - Google Patents

Pompe ayant une valve avec un dispositif d'amortissement Download PDF

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Publication number
EP2519744B1
EP2519744B1 EP11719157.7A EP11719157A EP2519744B1 EP 2519744 B1 EP2519744 B1 EP 2519744B1 EP 11719157 A EP11719157 A EP 11719157A EP 2519744 B1 EP2519744 B1 EP 2519744B1
Authority
EP
European Patent Office
Prior art keywords
valve
pump
valve body
damping arrangement
outlet
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.)
Not-in-force
Application number
EP11719157.7A
Other languages
German (de)
English (en)
Other versions
EP2519744A2 (fr
Inventor
Axel MÜLLER
Olaf OHLIGSCHLÄGER
Stefan Quast
Michael Feckler
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.)
Thomas Magnete GmbH
Original Assignee
Thomas Magnete GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Thomas Magnete GmbH filed Critical Thomas Magnete GmbH
Publication of EP2519744A2 publication Critical patent/EP2519744A2/fr
Application granted granted Critical
Publication of EP2519744B1 publication Critical patent/EP2519744B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • 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
    • F04B17/048—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors using solenoids the fluid flowing around 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
    • F04B17/046—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
    • F04B53/001—Noise damping
    • 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
    • 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
    • F04B2201/00—Pump parameters
    • F04B2201/06—Valve parameters
    • F04B2201/0604—Valve noise
    • 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
    • F04B2203/0406—Vibration
    • 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
    • F04B35/00—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for
    • F04B35/04—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for the means being electric
    • F04B35/045—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for the means being electric using solenoids

Definitions

  • the invention relates to a pump according to the preamble of claim 1.
  • DE 10 2006 019 584 A1 shows a designed as a reciprocating pump electromagnetic pump.
  • a check valve with a valve body is provided, which is firmly inserted between an outlet nozzle and a piston rod leading dosing and an outlet flange.
  • the disadvantage here is that impacts of the piston rod on the valve body cause noise and initiate vibrations in the entire pump.
  • EP 1 748 188 A1 shows an embodied as a reciprocating pump electromagnetic pump in which the outlet side, a check valve is provided. A valve body of the check valve is firmly inserted in a cooperating with a piston rod dosing. In the event of contact of the piston rod and the valve body undesirable vibrations and noises, which are mitigated by an intended Mzzidämpf description only inadequate.
  • the magnetic pump comprises a magnetically displaceable armature piston with a piston rod, which are displaced together upon excitation of a coil in the direction of the suction valve and discharge fluid when de-energized or suck in the suction valve.
  • the suction valve comprises a valve body, which is received axially non-displaceably in a receptacle of a core flange, and which has a central bore through which liquid can pass from an antechamber into a Fühngshotse leading the piston rod.
  • the disadvantage is that upon energization of the coil, the end face of the piston rod abuts against the valve body and thus noise and vibration in the pump be initiated. Furthermore, it is disadvantageous that when the coil is de-energized, the liquid is tracked exclusively via the central bore, so that a comparatively high negative pressure is established in the guide sleeve, which can form a counterforce to the return movement of the armature piston.
  • US 3 380 387 A which is considered to be the closest prior art, describes a designed as a reciprocating pump electromagnetic pump comprising a cylinder in which a check valve is slidably received with a valve body.
  • the check valve has a valve seat, in which a valve member formed as a ball is clamped by means of a first compression spring relative to the valve seat in a position closing a channel.
  • the channel opens into a arranged below the check valve cylindrical chamber whose volume is formed by a reciprocating piston and a bottom of the valve body.
  • a second compression spring braces the valve body against the cylinder and an adjusting device which allows a displacement of the check valve in the cylinder.
  • the position of the check valve determines the volume of the cylindrical chamber and thus the amount of fluid delivered per piston stroke.
  • WO 99 35 399 A1 describes a diaphragm pump comprising a valve disposed between a valve plate and a storage plate.
  • the valve has a valve body having first and second ends. Disposed in front of the first end is a first annular element separated from the valve body by a spacer, which receives a valve seat.
  • a spring receiving Within the valve body, a spring receiving, which receives a compression spring arranged. A displaceable in a recess of the spring receiving valve member is clamped in a closed valve position by the prestressed compression spring against the valve seat, which can occur by displacing the valve member against the spring force fluid in the conveying direction through the valve.
  • a second annular element Before the second end of the valve body, a second annular element is positioned, which with the second end of a Forming recess for receiving a resilient spacer ring.
  • the elastic spacer serves to compensate for joining forces during assembly of the valve between the valve plate and the storage disk.
  • DE 40 35 835 A1 describes a designed as a reciprocating pump electromagnetic pump, comprising a housing and an inlet nozzle, in which two heat-insulating plastic inserts, which receive a suction valve, are arranged.
  • the suction valve is arranged behind a suction chamber and comprises a valve body, a valve seat and a valve member, which is clamped by a compression spring against the valve seat, wherein displacing the valve member against the spring force fluid can pass in the conveying direction through the valve.
  • WO 2004 109 093 A1 describes a reciprocating pump comprising a valve disposed in a housing part of the pump.
  • the valve has a valve body screwed into the housing part, in which a valve member is slidably received with a valve stem, wherein the valve body and the housing part are sealed by a sealing element against a fluid.
  • the valve stem closes with an enlarged diameter extension, which is acted upon by a valve disposed in the valve body spring force, which clamps the extension in a closed position of the valve against a formed in the valve body valve seat, wherein displacing the valve member against the spring force fluid in Flow direction through the housing part and the valve body passing channel can flow through the valve.
  • the pump according to the invention which is preferably an electromagnetic pump, arranges a delivery space between an inlet and an outlet, a valve arranged to achieve a required pumping capacity between the inlet and the delivery space and / or between the delivery space and the outlet
  • the valve has a valve body whose valve seat in the outlet direction, ie in the conveying direction of the pump, points, so that the valve member cooperating with the valve member substantially prevents a return of funded fluid counter to the conveying direction.
  • the valve member is in this case biased against the valve seat to achieve a closed position, and are in the conveying direction by lifting against the bias of a spring, for example, the passage of fluid free.
  • the valve body is accommodated in a receptacle of a pump part, for example in a receptacle of a Kemflansches, a nozzle, or a received in one of said parts such as a socket or a guide sleeve.
  • the valve body with respect to the receiving it receiving axially displaceable during operation of the pump, so that the valve body can recede upon contact with a different from the valve movable part of the pump, in particular a piston rod or an armature piston of the drive.
  • the force or energy otherwise introduced into the valve body upon impact of the movable part does not become noises, vibrations, vibrations and / or heat but converted into an axial movement of the valve body.
  • the valve body is assigned a resilient damping arrangement which loads the valve body into a starting position.
  • the initial position of the valve body in this case corresponds to that, expediently by a stop in the receptacle of the pump part limited end position, which occupies the valve body with de-energized drive. If a piston rod is displaced in the direction of the valve body when the drive is energized, the valve body is able to follow the last part of the axial displacement of the piston rod under its load, wherein the resilient damping arrangement is elastically reversibly compressed, deformed or tensioned. After de-energizing the drive causes the Dämpfänowski in the manner of a spring, the provision of the valve body back to its original position.
  • the displacement of the valve body expediently makes less than half of the axial strength of the damping arrangement, so that it can be configured with a stiffness that reliably resets the valve body.
  • the axial displacement travel of the valve body and thus the amount of axial displacement does not exceed one quarter of the axial strength of the damping assembly, in particular not more than one-eighth.
  • the damping arrangement expediently has the same axial strength as the peripheral section of the valve body which is guided in the receptacle. The damping arrangement thus stores displacement energy of the piston rod and thus dampens noise and vibrations.
  • the return stroke of the piston rod already causes a negative pressure at the outlet-side end side of the valve body, depending on the arrangement of the valve in the case of a suction valve, the valve member lifts off from the valve seat, or, in the case of a check valve arranged on the outlet side, additionally sucks the valve member in the direction of the valve seat.
  • This vacuum can also - in addition to the Dämpfan extract or alone - be used as a restoring force for the axially displaceable valve body in total, since the negative pressure during the return stroke of the piston rod is formed, so that the negative pressure can reset the valve body in total.
  • a suction of the entire valve body favors
  • the damping arrangement comprises an elastomeric ring which may be formed in the manner of an O-ring or the like.
  • the elastomer ring is expediently supported at one end on a corresponding abutment surface of the valve body, and at the other end is supported on an abutment which is axially immovable relative to the receptacle receiving the valve body.
  • the steamer assembly further comprises other parts such as the elastomer ring
  • a damping plate which may be formed of plastic or metal and which may conveniently be arranged on the side facing away from the support surface of the Ventitkorpumpen side of the elastomeric ring.
  • the damping arrangement comprises a spring, such as a plate spring, which biases the valve body back to its original position.
  • the damping arrangement on the valve body, for example by fixing the damping arrangement to a section of the valve body in a positive-locking or force-locking manner.
  • the valve body on the Radial circumference where it is guided in the receptacle, equipped with a sliding coating or the like, such as Teflon, to avoid a tight pressing or tilting.
  • a sliding coating or the like such as Teflon
  • the abutment against which the damping arrangement is supported is expediently designed as a caulking ring which has a central hole through which one end of the valve body can protrude axially into an antechamber in the area of the pump upstream of the Kemflansch.
  • an eccentric perforation may be provided in the Verstemmring next to the central hole, which allows a fluid connection between the pre-chamber and an inner region of the pump or the Kemflansches, so that two ways for tracking are given by fluid in the interior of the pump. As a result, excessively high negative pressures are advantageously avoided.
  • valve body is encased in its radial receptacle with an elastomer material which allows axial mobility, but at the same time ensures an at least liquid-tight, preferably also gas-tight seal for receiving.
  • valve body In the case of a suction valve arranged on the inlet side, it is necessary to use the piston rod in the guide sleeve in order to create a negative pressure which lifts the valve member on the side of the valve body facing away from the inlet.
  • the axial mobility of the valve body thus allows the formation of the pump such that the piston rod comes into contact with the valve body and thus is particularly small-sized. Further, the axial distance between the valve body and piston rod is achieved in the range of zero, so that the negative pressure is reached early and reliably in the return of the piston.
  • a magnetic pump which is a through-flow type.
  • the pump has a modular design in a simple way and can be easily mounted thereby.
  • the pump comprises a magnetic drive which is accommodated in a housing 2, wherein the housing 2 surrounds a coil carrier 3, on which a coil 4 is wound. About a led out of the housing 2 connection area 5, the coil can be connected to a power supply.
  • an output flange 6 is on the output side clamped, which limits the output side of the housing 2 on the output side substantially and an outlet channel 7, through which the liquid to be conveyed is ejected. Dash-dotted with 8 a cap for the outlet channel 7 is shown.
  • the output flange 6 forms an outlet of the pump 1.
  • a magnet-guiding Kemflansch 9 is pressed into the housing, which has an inner portion of smaller diameter, which is insertable into the inner region of the bobbin 3, and which has an outer portion with a larger diameter which protrudes from the housing 2.
  • an inlet nozzle 10 is used on its side facing away from the housing 2, which has an inlet channel 11, can pass through the liquid to be supplied.
  • an external thread is provided on the outer circumference of the inlet nozzle 10, which allows the connection with an internal thread in a projecting annular region of the Kemflansches 9.
  • the inlet nozzle 10 is sealed against the Kemflansch 9 with a seal 12.
  • a one-piece filter 12a made of a plastic-coated mesh is inserted between the inlet nozzle 10 and the core flange 9, a one-piece filter 12a made of a plastic-coated mesh is inserted. Dash-dotted with 8 'a cap for the inlet port 11 is shown. The Kemflansch 9 and the inlet nozzle 10 form an outlet of the pump. 1
  • the output flange has an approximately cylindrical central recess 6a in which the armature piston 13 of a drive unit which consists of the armature piston 13 and a piston rod 14 fixed in a recess 13a of the armature piston 13 is received in an axially displaceable manner.
  • the armature piston 13 and the piston rod 14 are caulked together.
  • Fig. 1 is the anchor piston 13 in its assumed at deenergized coil 4 starting position.
  • the piston rod 14 has a continuous central bore 14b.
  • an insert member 60 is inserted, which has a cylindrical main portion 60a, which connects to a likewise formed as a flange mounting portion 60b.
  • the attachment portion 60b is caulked in a hollow cylindrical receptacle 13b of the armature piston 13 widened in relation to the recess 13a.
  • a tapered section 60c At the opposite side of the main section 60a from the attachment section 60b, it is continued by a tapered section 60c, which itself merges into a conical centering pin 60d.
  • sealing ring 61 sits in the joint area with the mounting portion 60b.
  • Another, identical to the sealing ring 61 sealing ring 62 is disposed at the mouth of the outlet channel 7 in the central recess 6a.
  • the two sealing rings 61, 62 abut each other, and the extension 60 penetrates a distance into the sealing ring 62, so that a largely dense separation of the outlet channel 7 from the central recess 6a.
  • the sealing rings 61, 62 dampen the stop of the moving parts.
  • the core flange 9 has a central recess 9a facing the inlet connector 10, and at its end facing the armature piston 13 a conically tapering receiver 9b adapted to the conical shape of the end facing away from the outlet of the armature piston 13, wherein the recess 9a and the cone receiver 9b are separated by a constricting, a through opening 9c releasing web portion 9d.
  • a guide sleeve 15 is inserted, which has a central bore 15d into which the piston rod 14 can penetrate.
  • a cylindrical annular portion 15e of the guide sleeve 15 projects into the web region 9d and thus centers the guide sleeve in the through-opening 9c.
  • the guide sleeve 15 has a radial inlet 15a, which opens into a ring sprocket area 16 between the Kemflansch 9 and the guide sleeve 15 and thus a connection between an inner region 15b of the guide sleeve 15 and the annular gap 16 produces.
  • the guide sleeve 15 also has a recess 15c facing the inlet nozzle 10 in the form of an annular step widening the bore 15d into which a valve arrangement 17, which will be explained in more detail below, can be inserted. In Fig. 2 this area of the pump 1 is enlarged and thus better visible.
  • the recess 15c forms a receptacle for the valve 17, which is provided in a pump part, in the present case the guide sleeve 15. It is understood that such a receptacle can also be provided in another pump part.
  • a compression spring 18 which rests with its opposite end against a shoulder 13b defining end portion of the armature piston 13 and thus biases the armature piston 13 in the outlet direction.
  • the central bore 14b of the piston rod 14 creates in the region not filled by the insert member 60, a fluid connection between the inner region 15b and a delivery chamber 19 which is bounded by the output flange 6, the core flange 9 and the bobbin 3 of the housing 2.
  • the piston rod 14 radial connection holes 14a, which establishes a connection between the central bore 14b of the piston rod 14 and the delivery chamber 19 in the region of the inlet facing the end face of the armature piston 13.
  • a ring step 60f of the insert member 60 is formed as a helical spring, the centering pin 60d surrounding return spring 21, which supports a valve ball 22 against a valve seat 23 which is provided in the outlet side end face of the central bore 14b of the piston rod 14.
  • the valve seat 23 has a Flanschforrn and is so pressed into the central bore 14b, that its end face with the inlet-side end face of the piston rod 14 is aligned and not axially projecting therefrom.
  • the valve assembly 17 is designed as a suction valve and has a valve body 30, which has a central through-bore valve 30 a, in which a valve member plunger 31 is axially displaceable.
  • a valve seat 32 On a side facing the armature piston 13 end face of the valve body 30 is a valve seat 32 defining recess, which is lined with an elastomeric material 35 is formed.
  • the elastomeric material 35 coats the valve seat, but at the same time forms a Anschlagdämpf constitutional 35 a for the incident upon actuation of the pump inlet side end face of the piston rod 14th
  • this has a radially outwardly widening stop surface 31a, which is greater than the valve bore 30a of the valve body 30 and thus forms a valve member for closing the valve assembly, if this under the bias of a coil spring trained preload spring 33 is pulled against the valve seat 32.
  • the preload spring 33 is supported with one end against an annular portion 30b of the valve body 30 and the other end against a lug portion 34 which is connected to the armature piston 13 facing away from the end face of the valve member plunger 31 from.
  • Vorlabel 33 acts on the attachment part 34 and the valve member plunger 31, the valve member 31 a in the direction of the valve seat 32 in a closed position, so that the Ventilanordung 17 forms a check valve against the inlet direction.
  • This design of the valve assembly 17 has the advantage that at least in the closed state of the valve assembly 17, the valve member 31 a does not project beyond the piston rod side end face of the valve body 30.
  • a Verstemmring 36 is caulked radially in a step 10d of the inlet nozzle 10 and thus forms a non-positive abutment against sliding out of the guide sleeve 15 from the recess 10a.
  • the caulking ring 36 has a central hole 36a, through which the valve body 30 projects in the direction of the inlet nozzle 10, and an eccentric perforation 37, which for a fluid connection in a radial region to the Annular gap 16 is determined.
  • a fluid connection between the annular gap 16 and the perforation 37 takes place through a connecting region 16a.
  • a damper assembly 40 Disposed between the caulking ring 36 and a step 30a of the valve body 30 is a damper assembly 40 having an elastomeric ring 41 (in FIG Fig. 2 A radial projection 42a of the damping plate 42 penetrates between the end face of the sliding sleeve 15 and the caulking ring 36. A radial extension 42a of the damping plate 42 penetrates in this case, which is supported directly on the step 30a, and a plastic molded damping plate 42 which bears against the Verstemmring 36 ,
  • the damping plate 42 may also be made of metal or other material suitable as a spacer. In particular, it is also possible to completely dispense with appropriate dimensioning of the elastomeric ring 41 on the damping plate 42.
  • the valve body 30 has a cylindrical lateral surface portion 30c, which is adapted to the diameter of the recess 15c, wherein the outer diameter of the lateral surface portion 30c with the damping assembly 40 is approximately aligned
  • the lateral surface portion 30c is not caulked in the recess 15c, but axially to this displaced. Due to its elastic property, the damping arrangement 40 in this case biases the valve body 30 in the direction of the outlet against the corresponding annular shoulder 15f of the guide sleeve 15. It is possible to form the damping arrangement 40 as a spring member. Alternatively, it is also possible to inject the damping arrangement 40 completely or partially to the valve body 30.
  • Fig. 3 is an alternative embodiment to the Fig. 1 and 2 represented in the same reference numerals as in Fig. 1 and 2 designate the same or structurally comparable parts.
  • the elastomeric lining of the recess defining the valve seat 32 and the stopper damper surface 35a are not formed of a one-piece elastomeric material 35, but are a separate one forming a stopper damper surface 35a ' and from the elastomeric material 35 different insert 70 with a support body 71 made of metal or plastic and a thereon applied elastomer sheath 72 with a Dehnungsringaus Principleung 72a provided for this purpose.
  • the elastomer sheathing 72 is vulcanized or shrunk onto the carrier body 71 and surrounds it in particular radially as well as on the end face facing the piston rod 14.
  • the insert 70 has a through opening. This can improve the tightness of the suction valve, since the elastomer material 35 of the valve seat 32 is then not mechanically stressed by impacts.
  • the armature piston 13 When the coil 4 is energized, the armature piston 13 is displaced together with the piston rod 14 in the direction of the inlet port 10. By the liquid jammed in the inner region 15 b, the valve ball 22 is returned against the bias of the return spring 21 and the liquid penetrates into the central bore 14 b of the piston rod 14, and passes through the radial connection holes 14 a in the delivery chamber 19. If the coil 4 now de-energized, under the bias of the spring 18, the armature piston 13 is displaced together with the piston rod 14 in the direction of the output flange 6, the overflow valve 22/23 closes and the liquid acted upon by the return stroke in the delivery chamber 19 is forced into the outlet channel 7.
  • valve assembly is designed as a suction valve on the inlet side of the pump 1. It is understood that the valve arrangement can also be arranged as a check valve on the outlet side of the pump, in which case the damping arrangement on the side of the valve seat and the Anschlagdämpf materials 35 a are provided on the valve seat opposite side of the valve body.

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

Claims (8)

  1. Pompe pour refouler un liquide, comprenant:
    une entrée,
    une sortie, et
    un espace de refoulement,
    une soupape (17) étant disposée entre l'entrée et l'espace de refoulement ou entre l'espace de refoulement et la sortie,
    la soupape (17) présentant un corps de soupape (30) avec un siège de soupape (32) tourné dans la direction de la sortie et un organe de soupape (31 a) coopérant avec le siège de soupape (32),
    l'organe de soupape (31 a) étant sollicité avec précontrainte contre le siège de soupape (32) dans une position fermée de la soupape (17) et laissant passer du fluide dans la direction de refoulement par soulèvement de l'organe de soupape (31 a) à l'encontre de la précontrainte,
    le corps de soupape (30) étant reçu de manière déplaçable axialement dans un logement (15c) d'une partie de pompe (15),
    caractérisée en ce
    qu'un agencement d'amortissement flexible (40) est associé au corps de soupape (30), lequel sollicite le corps de soupape (30) dans une position de départ, l'agencement d'amortissement (40) comprenant une bague élastomère (41) ou une enveloppe au moins partielle du corps de soupape (30) en matériau élastomère.
  2. Pompe selon la revendication 1, caractérisée en ce que l'agencement d'amortissement (40) comprend un ressort.
  3. Pompe selon l'une quelconque des revendications 1 ou 2, caractérisée en ce que l'agencement d'amortissement (40) est fixé sur le corps de soupape (30).
  4. Pompe selon l'une quelconque des revendications 1 à 3, caractérisée en ce que l'agencement d'amortissement (40) s'appuie contre une butée (37) retenue de manière immobile axialement dans le logement (15c) de la partie de pompe.
  5. Pompe selon l'une quelconque des revendications 1 à 4, caractérisée en ce que la soupape (17) est une soupape d'aspiration du côté de l'entrée.
  6. Pompe selon l'une quelconque des revendications 1 à 4, caractérisée en ce que la soupape (17) est une soupape de non retour du côté de la sortie.
  7. Pompe selon l'une quelconque des revendications 1 à 6, caractérisée par un entraînement électromagnétique avec une tige de piston (14) qui est décalée axialement dans la direction du corps de soupape (30).
  8. Pompe selon l'une quelconque des revendications 1 à 7, caractérisée en ce que l'agencement d'amortissement (40) permet un décalage axial du corps de soupape (30),
    l'agencement d'amortissement (40) comprenant une plaque d'amortissement (42) qui s'appuie contre une bague de matage (36).
EP11719157.7A 2010-03-26 2011-03-18 Pompe ayant une valve avec un dispositif d'amortissement Not-in-force EP2519744B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102010013106A DE102010013106A1 (de) 2010-03-26 2010-03-26 Pumpe
PCT/DE2011/000284 WO2011116752A2 (fr) 2010-03-26 2011-03-18 Pompe

Publications (2)

Publication Number Publication Date
EP2519744A2 EP2519744A2 (fr) 2012-11-07
EP2519744B1 true EP2519744B1 (fr) 2013-07-24

Family

ID=44510613

Family Applications (1)

Application Number Title Priority Date Filing Date
EP11719157.7A Not-in-force EP2519744B1 (fr) 2010-03-26 2011-03-18 Pompe ayant une valve avec un dispositif d'amortissement

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US (1) US9464628B2 (fr)
EP (1) EP2519744B1 (fr)
CN (1) CN102918267B (fr)
DE (1) DE102010013106A1 (fr)
RU (1) RU2527928C2 (fr)
WO (1) WO2011116752A2 (fr)

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DE102012009952B3 (de) * 2012-05-18 2012-11-15 Thomas Magnete Gmbh Elektromagnetische Hubkolbenpumpe mit einer vor Beschädigungen durch ein Einfrieren des Arbeitsfluids geschützten Kolbenstange
DE102012012779A1 (de) * 2012-06-25 2014-03-27 Thomas Magnete Gmbh Elektromagnetische Pumpe
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WO2015031884A1 (fr) 2013-08-30 2015-03-05 Flow Control Llc. Pompe de portion à haute viscosité
DE102014211895A1 (de) * 2014-06-20 2015-12-24 Robert Bosch Gmbh Verfahren und Vorrichtung zur Ansteuerung einer Hubkolbenpumpe
DE102015201463A1 (de) 2015-01-28 2016-07-28 Robert Bosch Gmbh Verfahren zum Betreiben einer Kolbenpumpe, einer Steuereinrichtung und Kolbenpumpe
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DE102020131796A1 (de) 2020-12-01 2022-06-02 Alfred Kärcher SE & Co. KG Kolbenpumpe für ein hochdruckreinigungsgerät

Also Published As

Publication number Publication date
RU2012145471A (ru) 2014-05-10
DE102010013106A1 (de) 2011-09-29
WO2011116752A3 (fr) 2012-03-01
CN102918267A (zh) 2013-02-06
CN102918267B (zh) 2016-08-31
RU2527928C2 (ru) 2014-09-10
EP2519744A2 (fr) 2012-11-07
US9464628B2 (en) 2016-10-11
US20130034459A1 (en) 2013-02-07
WO2011116752A2 (fr) 2011-09-29

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