EP0484773B1 - Distributeur de fluide - Google Patents

Distributeur de fluide Download PDF

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Publication number
EP0484773B1
EP0484773B1 EP91118296A EP91118296A EP0484773B1 EP 0484773 B1 EP0484773 B1 EP 0484773B1 EP 91118296 A EP91118296 A EP 91118296A EP 91118296 A EP91118296 A EP 91118296A EP 0484773 B1 EP0484773 B1 EP 0484773B1
Authority
EP
European Patent Office
Prior art keywords
valve
stroke
pump
delivery
pressure
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.)
Expired - Lifetime
Application number
EP91118296A
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German (de)
English (en)
Other versions
EP0484773A1 (fr
Inventor
Karl-Heinz Fuchs
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.)
Aptar Radolfzell GmbH
Original Assignee
Erich Pfeiffer GmbH
Ing Erich Pfeiffer 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 Erich Pfeiffer GmbH, Ing Erich Pfeiffer GmbH filed Critical Erich Pfeiffer GmbH
Publication of EP0484773A1 publication Critical patent/EP0484773A1/fr
Application granted granted Critical
Publication of EP0484773B1 publication Critical patent/EP0484773B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B05—SPRAYING OR ATOMISING IN GENERAL; APPLYING FLUENT MATERIALS TO SURFACES, IN GENERAL
    • B05B—SPRAYING APPARATUS; ATOMISING APPARATUS; NOZZLES
    • B05B11/00—Single-unit hand-held apparatus in which flow of contents is produced by the muscular force of the operator at the moment of use
    • B05B11/01—Single-unit hand-held apparatus in which flow of contents is produced by the muscular force of the operator at the moment of use characterised by the means producing the flow
    • B05B11/10—Pump arrangements for transferring the contents from the container to a pump chamber by a sucking effect and forcing the contents out through the dispensing nozzle
    • B05B11/1001—Piston pumps
    • B05B11/1016—Piston pumps the outlet valve having a valve seat located downstream a movable valve element controlled by a pressure actuated controlling element
    • B05B11/1018—Piston pumps the outlet valve having a valve seat located downstream a movable valve element controlled by a pressure actuated controlling element and the controlling element cooperating with means for opening or closing the inlet valve
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B05—SPRAYING OR ATOMISING IN GENERAL; APPLYING FLUENT MATERIALS TO SURFACES, IN GENERAL
    • B05B—SPRAYING APPARATUS; ATOMISING APPARATUS; NOZZLES
    • B05B11/00—Single-unit hand-held apparatus in which flow of contents is produced by the muscular force of the operator at the moment of use
    • B05B11/01—Single-unit hand-held apparatus in which flow of contents is produced by the muscular force of the operator at the moment of use characterised by the means producing the flow
    • B05B11/10—Pump arrangements for transferring the contents from the container to a pump chamber by a sucking effect and forcing the contents out through the dispensing nozzle
    • B05B11/1087—Combination of liquid and air pumps

Definitions

  • the invention relates to a discharge device according to the preamble of claim 1. It is provided for at least one medium or for flowable media of essentially any physical state.
  • the discharge device can be operated to discharge at least one medium via a pressure source, for example a pressure accumulator, and thus only by manually opening one Exhaust valves are actuated, but expediently has a pump with a pump chamber for at least one medium, which is narrowed by manual force to convey the medium.
  • the discharge device is preferably designed for one-handed use, the forces to be applied for the discharge being expediently only generated manually.
  • the funding of at least one medium can be controlled for different purposes depending on the stroke.
  • an outlet valve can only be opened by a stop at the end of the stroke in order to achieve a high discharge pressure.
  • a pressure relief can also be provided at the end of the stroke, for example by unsealing a pump piston be provided to end the media funding as suddenly as possible.
  • control means are conceivable for conveying a further medium, for example compressed gas, which is discharged in addition to a first medium, before the start and / or after the end of the conveyance of the first medium through the discharge opening or the like, or for conveying the first and / or at least one discharge of the medium after a partial stroke after the start of the stroke.
  • control means can be provided in order to convey at least a part of the conveyed further medium directly to a discharge nozzle and / or at least a part at a greater distance in front of it directly into an outlet channel leading to this discharge nozzle or to the discharge opening.
  • This allows the media to be mixed at any point and / or e.g. are promoted sequentially for cleaning the outlet channel and the nozzle or for other purposes.
  • the invention is further based on the object of providing a discharge device of the type mentioned, by means of which disadvantages of known designs are avoided or effects of the type described can be achieved and which, in particular, ensures very precise control of the media delivery of at least one medium with a simple design.
  • this free path is used to build up a delivery pressure of at least one second medium and / or to open a pressure-dependent outlet valve for this second medium.
  • This can e.g. Compressed air is initially biased in a pump chamber via the idle path and then advanced by opening the outlet valve, after which the first, e.g. liquid medium is also conveyed to the discharge opening.
  • the delivery of the second medium can then take place continuously up to the end of the stroke of the actuation and, if necessary, a short time beyond, while the delivery of the first medium has already stopped before the end of the stroke.
  • the mechanical control enables a very precise mutual adjustment of these functional sequences.
  • the pressure in the pump chamber is expediently changed by opening and closing a slide-controlled control valve between a discharge pressure reaching for the discharge to the discharge opening and a pressure not sufficient for this, the valve outlet of this at least one control valve not leading to the outlet channel or to the outlet opening, but leads back to a media store via a return channel.
  • No separate return channel is required for this if the inlet or suction channel for the pressure chamber is also used as the return channel becomes.
  • no separate control valve is required if it is formed by a path-dependent controlled inlet valve for the pressure chamber, for which then no pressure-dependent inlet valve is required.
  • the movable valve body of the inlet valve if it is formed by a pump piston, in particular a pre-suction piston of the pump.
  • the medium is deflected twice in opposite directions, namely first in the discharge direction from the pump chamber and then in the opposite direction into the return channel.
  • the design according to the invention is particularly suitable for discharge devices according to DE-A-37 15 301, to which reference is made for further details and effects.
  • the first empty or partial stroke is expediently more than a ninth to a quarter or a third of the total stroke and can also correspond to approximately half of the total stroke.
  • the corresponding piston does not need to be guided with its inner circumference sealed to an inlet channel which projects substantially freely into the pump chamber, the inner circumference of the piston having a corresponding ring distance from the outer circumference of the inlet channel, the inlet channel in the jacket can be provided with through openings and / or can have longitudinal channels on the outer circumference via the associated longitudinal section.
  • the piston runs close to the outer circumference of the inlet channel, which in this area has no through openings or slots or an enlarged collar.
  • the component which determines the control characteristic of the control means and which is designed, for example, in the manner of a control curve can, is expediently formed by a part separate from an associated support or base body, so that the control characteristic can be changed as desired by selecting this component.
  • the component can, for example, only be fastened by a plug and / or snap connection or fixed in the fastening position by a retaining spring.
  • the control valve expediently lies essentially entirely within the pump chamber.
  • the passage cross section of the return channel can be changed depending on the stroke, e.g. in that, following a first partial stroke into the return duct, a mandrel and / or part of a spring, e.g. a helical spring, which means that the return channel, which is free at the start of the stroke, is limited to a ring channel after a first short partial stroke and before the control valve closes.
  • the return channel limited in this way which can also be helical due to the spring, then forms a return throttle, so that a pressure is built up in the pressure chamber by the time the control valve closes, but its level is lower than the discharge pressure required for delivery into the outlet channel.
  • the discharge device is expediently designed in accordance with DE-A-37 22 469, to which reference is made for further details and effects.
  • the control means for the first, usually non-compressible medium can be designed such that at least one pump pulse is generated during the essentially continuous conveying of the second medium, with which the first medium is supplied to the second medium.
  • a very fine atomization of an active ingredient can also be achieved by the inventive design.
  • the second medium is expediently discharged by pressure-dependent opening an associated output valve so that the conveying speed of this medium does not fall below a predetermined value.
  • the discharge device 1 which is essentially assembled from injection-molded plastic parts, is used for essentially sealed placement on the neck of a storage device, from which, with each return stroke, a certain amount of a medium is drawn in via a riser pipe by a discharge unit 3. It also has, from the atmosphere, bypassing a thrust piston pump 5 of the discharge unit 3, conveying means 4 for compressed air, which are essentially formed by a thrust piston pump 6 arranged on the same base body 2 in the same axis as the pump 5. Both pumps 5, 6 are essentially simultaneous with a common actuation 7 via a discharge and Actuate actuating head 8 by finger pressure so that a push actuation is transmitted to the pump movement.
  • the actuating head 8 has a discharge opening 9 opening into the open, which, influenced by control means 10, is connected to the discharge unit 3 via an outlet channel 11 and via a separate channel which opens near it to the conveyor 4 closer to it.
  • a cylinder housing 12 which is formed in one piece with the base body 2 accommodates a piston unit 13 which is formed by two separate pump pistons 14, 15 of the discharge unit 3 which are axially movable with respect to one another and constantly mesh with one another.
  • the inner circumference of the pump piston 14 projecting in the direction of the pump stroke by about half its length over the other pump piston 15 is assigned an outer circumferential surface as piston raceway 16.
  • the inner circumference of the cylinder housing 12 forms a cylinder raceway 17 for the sealed abutment of the front end of the pump piston 15, which, like the pump piston 14, is cup-shaped, but is considerably shorter.
  • An annular gap is formed between the cylinder race 17 and the outer circumference of the front, enlarged section of the pump piston 14 as well as between the inner circumference of the pump piston 15 and the outer circumference of the pump piston 14; the successive annular gaps represent a line connection for the outlet channel 11.
  • the cylinder housing 12 forms an inlet, through which the pump 5 draws in from the reservoir through a riser pipe and via which it, controlled by the control means 10, can convey back into the reservoir .
  • This inlet forms a substantially completely within the cylinder housing 12 and the cylinder race 17 and essentially in line with these lying inlet and return channel 18, the flow cross-section can be changed depending on the stroke.
  • the channel 18 is delimited by a sleeve 19 projecting essentially freely and coaxially into the cylinder housing, the outer circumference of which has a radial distance from the cylinder race 17 and forms a control valve 20 with an inner sealing lip 21 at the front end of the pump piston 14.
  • the sealing lip 22 running on the piston raceway 17 is located at the front end of the pump piston 15.
  • the outer circumference of the sleeve 19 forms a valve seat 23 between the ends and only over a part of its length run over by the sealing lip 21 for the sealingly displaceable contact of the sealing lip 21.
  • the sleeve 19 is on the associated section with a radial against the cylinder track 17 projecting collar 24 provided.
  • the sections 27, 28 located adjacent to the collar 24 can have essentially the same outer width, which is approximately constant through to the respective associated end, such that an annular gap is delimited between them and the sealing lip 21.
  • the same outside width also has a plug-in section 29 formed by a front end, with which the sleeve 19 is inserted in a tightly adapted manner, narrowed relative to the cylinder race 17 and adjoining it via an annular shoulder, with an opening of the cylinder housing 17 which is limited in terms of stops.
  • the slide or piston 14 forms with the sleeve 19 a throttle 30, the flow cross section of which changes depending on the path with the position of the pump piston 14.
  • the jacket of the pump piston 14 is so narrowed at a distance behind the sealing lip 21 on the inner circumference that with the outer circumference of the section 27 it can limit an annular gap which is narrower than the annular gap in the region of the sealing lip 21.
  • a prestressed helical compression spring 32 is fitted snugly onto the outer circumference of the mandrel 31 and is provided as the only spring for all resetting functions of the discharge unit 3 and for the pump resetting of the conveying means 4.
  • the other end of the spring 32 is supported on an annular shoulder within the plug-in section 29 and therefore presses the sleeve 19 connected to the riser pipe into its stop position.
  • the outer circumference of the spring 32 lies closely against the inner circumference of the channel 18. In the starting position according to FIGS. 1 and 2, the free end 33 of the sleeve 19 lies within the pump piston 14 at a short distance behind the sealing lip 21 and at a short distance from the front end of the mandrel 31.
  • the pump piston 14 is moved over a first partial stroke 38 corresponding to this distance, the front end of the mandrel 31 penetrates into the channel 18, so that a helical channel which is essentially closed in cross section over the outer circumference is penetrated by the windings of the spring 32 lying therebetween is limited within the sleeve 19 and then to the end 33, the flow cross section of which can be smaller than that of the annular gap in the region of the sealing lip 21.
  • the partial stroke 38 lies at the beginning of a first partial stroke 34, which is required until the sealing lip 21 has reached the beginning of the inclined surface 25.
  • the annular gap in the area of the sealing lip 21 becomes continuously narrower until the sealing lip 21 runs onto the inclined surface 25 and thereby the connection between the channel 18 and the annular pressure chamber 39 closes.
  • the end 33 of the sleeve 19 enters the narrowed section of the pump piston 14, so that both parts can be brought together and liquid in the hollow pump piston 14 can be pressed further through the channel 18 back into the reservoir.
  • the sealing lip 21 then reaches the cylindrical valve seat 23 under radial prestress, which determines the next subsequent partial stroke 36 and via which a delivery or discharge pressure is now built up in the pressure chamber 39.
  • the medium can be conveyed from the pressure chamber 39 via the annular gaps mentioned on the outer circumference of the pump piston 14 to the outlet channel 11.
  • the line connection between the now substantially narrowed pressure chamber 39 and the channel 18 can again be throttled, opened or closed.
  • the line connection is opened here when the outer circumference of section 27 is smaller than the narrowed inner circumference of pump piston 14 because an annular passage gap is then provided.
  • the line connection is closed when the outer width of section 27 is approximately the same size as the narrowed inner circumference. Since a right-angled or at most obtuse conical shoulder 26 adjoins the corresponding end of the valve seat 23, the annular gap between the sealing lip 21 is suddenly opened when this end is passed over. From this end, the last partial stroke 37 takes place until the pump piston 14 strikes the end 33 of the sleeve 19 and the sealing lip 21 is still a short distance from the floor or the associated annular shoulder of the pressure chamber 39.
  • outlet valve 40 In the region of the interior, at the end of the outlet channel 11 adjoining the interior of the pump piston 15, there is an outlet valve 40, which is biased by the spring 32 to the closed position and whose valve parts can be moved relative to one another on the two pump pistons 14, 15.
  • the conical valve body 44 is formed in one piece with the end wall 42, which closes the pump piston 14 on the narrowed, cylindrical piston section 41, and its base projects beyond the outside thereof.
  • the end 33 abuts on the inside of this end wall 42 and the spring 32 is supported.
  • the narrower end of the valve body 44 merges in one piece into a shaft 46 which extends over the major part of the length of the outlet channel 11 and which is mounted by being inserted into a central channel of a piston rod 47 and with it delimits a section of the outlet channel 11 which is annular in cross section.
  • the pump piston 14 is thus centered only by the valve body 44 relative to the other pump parts and can then be guided on the corresponding partial strokes 35 to 37 by guiding on the inclined surface 25, on the valve seat 23 and / or on the section 27, so that also at open outlet valve 40 accurate centering is ensured.
  • the outlet valve 40 is adjusted so that it opens against the force of the spring 32 when the sealing lip 21 runs on the valve seat 23, so that the medium is then pumped out of the pressure chamber 39 to the discharge opening 9.
  • the pressure chamber 39 is relieved of pressure by returning it into the channel 18, so that the opening pressure acting on the rear end faces of the pump piston 14 is relieved.
  • the delivery ends after the end of the partial stroke 37 because the air compressed in the pump chamber 51 of the pump 6 continues to flow even after the end of the actuation until a pressure limit value is reached.
  • the pump chamber 51 is of a on the base body 2 with a snap connection in the essentially fixed pump piston 48 and a pump cylinder 49, which is formed by the jacket of the actuating head 8.
  • the pump piston 48 is penetrated by the outlet channel 11 or by the actuating plunger 47.
  • a pressure-dependent output valve 50 is provided, which opens after a first partial stroke and before the partial stroke 36 is reached.
  • the discharge device can be inserted and installed from one side of the base body 2, namely from the open side of the cylinder housing 12, by plugging. Since the pump pistons 14, 15 have essentially flat end walls 42, 43 and the valve seat 45 lies approximately in the plane of the inside of the end wall 43, very compact dimensions are also achieved for the piston unit 13.
  • the pump pistons 14, 15 have essentially only cylindrical outer and / or inner shapes in the jacket region.
  • the pump piston 48 is fastened with a snap connection and forms a closure for the rear mounting opening of the cylinder housing 12.
  • the discharge device can also have, in a simple manner behind the sealing lip 22 which is in the starting position, an aeration 52 for the storage vessel which is fed via the pump chamber 51 and which, at least in the starting position, is tightly closed by a ventilation valve 53.
  • the end wall 43 of the pump piston 15 forms on its outside a one-piece, conical valve body, which is pressed under the force of the spring 32 against a valve seat, the closing force being transmitted essentially only via the valve parts of the exhaust valve 40 lying against one another.
  • the valve seat is expediently formed by a sleeve 54 of the pump piston 48 which engages in the rear, enlarged end of the cylinder housing 12 and is penetrated by the actuating plunger 47, so that it can be made of a relatively soft material.
  • the annular ventilation channel leads from the pump chamber 51 between the sleeve 54 and the actuating tappet 47 to the ventilation valve 53 and from there adjacent to the pump piston 15 across the jacket of the cylinder housing 12 into an annular gap which is between the outer periphery of the rear end of the cylinder housing 12 and the inner periphery one of the flange sleeve 55 of the base body 2 which surrounds this at a radial distance is formed.
  • On this flange sleeve 55 a cap 56, for example a screw and / or plug cap for attaching the discharge device 1 to the bottle neck or the like.
  • the memory can also be flexibly connected to the discharge device.
  • the storage space of the storage vessel can be pressurized with the pump 6, so that when the pump 5 begins to return, the stored medium is pressed through the channel 18 into the pressure chamber 39 or at least the suction of the medium is supported.
  • the control means 10 described result in a pressure build-up that gradually approaches the outlet pressure of the outlet valve 40, so that the opening of the outlet valve 40 is reached very quickly at the beginning of the partial stroke 36.

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  • Details Of Reciprocating Pumps (AREA)
  • Containers And Packaging Bodies Having A Special Means To Remove Contents (AREA)
  • Reciprocating Pumps (AREA)
  • Coating Apparatus (AREA)
  • Closures For Containers (AREA)
  • Air Transport Of Granular Materials (AREA)
  • Electrical Discharge Machining, Electrochemical Machining, And Combined Machining (AREA)
  • Photographic Developing Apparatuses (AREA)

Claims (10)

  1. Distributeur (1) de fluides, avec un corps de base (2) pour au moins une unité (3) de distribution de fluides qui, par un actionneur (7), peut être actionnée entre un début de course et une fin de course d'une course d'actionnement, des moyens de commande (10), destinés à agir sur le refoulement de fluide à partir d'une chambre de refoulement (39), présentant au moins une soupape de commande (20) se fermant au moins une fois sur ladite course et pourvue d'une face de commande (23) et d'un passage de soupape, caractérisé en ce qu'une course à vide (38, 34) est prévue jusqu'au début de la fermeture de la soupape de commande (20) par rétrécissement du passage de soupape, en ce que la face de commande (23) est formée par un collet en saillie (24), et en ce que le collet (24) commande la fermeture de la soupape de commande (20).
  2. Distributeur selon la revendication 1, caractérisé en ce que les moyens de commande (10) sont prévus pour interrompre au moins deux fois en fonction de la course le refoulement de fluide entre le début et la fin d'une course d'actionnement, et en ce que, notamment, le refoulement de fluide est interrompu sur la course partielle et à vide (38, 34) faisant suite au début de course et/ou sur une course partielle (37) s'étendant jusqu'à la fin de course, ou encore est mis en marche sur la course partielle de liaison (35, 36), les moyens de commande (10) étant de préférence prévus pour le relâchement de la pression de la chambre de refoulement (39) sur au moins une course partielle (34, 37) par ouverture d'un refoulement de retour pour le fluide provenant de la chambre de refoulement (39).
  3. Distributeur selon la revendication 1 ou 2, caractérisé en ce que les moyens de commande (10) présentent au moins une soupape de commande (20) du genre tiroir s'ouvrant au moins deux fois en fonction de la course et se fermant au moins une fois sur la course d'actionnement, telle qu'une soupape d'admission pour la chambre de refoulement (39), soupape qui est notamment formée par une voie de déplacement de piston (16) et une lèvre d'étanchéité de piston (21), se déplaçant en ouverture et fermeture sur cette voie, d'un piston d'une unité de piston (13), et en ce que, de préférence, la soupape de commande (20) présente, comme siège de soupape (23) essentiellement fixe par rapport au corps de base (2), une face d'enveloppe sur une périphérie extérieure et, comme corps de soupape mobile, une douille de commande s'appliquant contre le siège de soupape (23) au moins en position de fermeture, un canal de soupape (18) étant notamment dirigé hors de la chambre de refoulement (39) à l'intérieur de la périphérie extérieure, et/ou étant formé par un canal d'admission (18) de la chambre de refoulement (39).
  4. Distributeur selon une des revendications précédentes, caractérisé en ce que les moyens de commande (10) sont conçus pour une augmentation progressive ou encore échelonnée de la pression dans la chambre de refoulement (39) et/ou pour un brusque relâchement de la pression de la chambre de refoulement (39), en ce que, notamment, le siège de soupape (23) présente une face de commande (25) montante en oblique vers une extrémité d'une face de fermeture de soupape et, à l'autre extrémité de la face de fermeture de soupape, un épaulement étagé (26), et en ce que, de préférence, au moins un organe de commande des moyens de commande (10) qui détermine l'interruption en fonction de la course, est formé par une pièce séparée du corps de base (2), notamment d'un seul tenant et/ou fixée par un assemblage à emboîtement (29), ou encore est réalisé sous la forme d'une douille (19) faisant librement salle dans une enveloppe cylindrique, douille qui présente un collet élargi (24) sur sa périphérie extérieure.
  5. Distributeur selon une des revendications précédentes, caractérisé en ce que la chambre de refoulement (39) est délimitée au moins pour partie annulairement et sur la périphérie intérieure par une douille (19) formant une admission, douille dont la périphérie extérieure forme de préférence la soupape de commande (20) par une lèvre d'étanchéité intérieure (21), la périphérie intérieure radialement extérieure de la chambre de refoulement (39) étant conçue comme voie de déplacement cylindrique (17) pour une lèvre d'étanchéité extérieure (22) de l'unité de piston (13) qui est disposée environ coaxialement à la lèvre d'étanchéité intérieure (21) et notamment à distance en arrière de cette dernière.
  6. Distributeur selon une des revendications précédentes, caractérisé en ce que les moyens de commande (10) présentent, pour un refoulement de retour hors de la chambre de refoulement (39) et/ou pour une montée en pression échelonnée dans la chambre de refoulement (39), au moins un étranglement (30) modifiable en fonction de la course, qui est de préférence pourvu d'organes pouvant être déplacés l'un dans l'autre afin de former une fente annulaire de refoulement de retour.
  7. Distributeur selon une des revendications précédentes, caractérisé en ce que la chambre de refoulement (39) est raccordée à un canal d'évacuation (11) ou encore une ouverture de distribution (9) par une soupape d'évacuation (40) s'ouvrant en fonction de la pression, dont les éléments de soupape sont notamment formés par deux pistons (14, 15) d'une unité de piston (13) qui peuvent être déplacés l'un vers l'autre contre la force d'un ressort de rappel (32) et qui présentent la lèvre d'étanchéité intérieure (21) et la lèvre d'étanchéité extérieure (22), les moyens de commande (10) étant de préférence conçus pour la fermeture en fonction de la course de la soupape d'évacuation (40) qui est notamment exclusivement ouverte lorsque la soupape de commande (20) est fermée, et/ou la soupape d'évacuation (40) se trouvant essentiellement dans la face de fond d'un piston arrière (15) en forme de coupelle, qui s'étend notamment, par une enveloppe de piston essentiellement cylindrique, approximativement jusqu'à un épaulement annulaire sur la périphérie extérieure du piston avant (14).
  8. Distributeur selon une des revendications précédentes, caractérisé en ce que des moyens de refoulement (4) sont prévus pour la distribution d'au moins un deuxième fluide, tel que de l'air comprimé, et en ce que les moyens de commande (10) sont notamment prévus pour produire un à-coup de pompage hors de la chambre de refoulement (39) entre un début de refoulement, éventuellement fonction de la pression, et une fin de refoulement des moyens de refoulement (4), les moyens de refoulement (4) devant de préférence être actionnés conjointement avec l'actionneur (7) et étant notamment formés par une deuxième pompe (6) disposée essentiellement coaxialement à une pompe de fluide (5), la deuxième pompe (6) étant raccordée au canal d'évacuation (11) au voisinage proche de l'ouverture de distribution commune (9) par l'intermédiaire d'une soupape de sortie (50).
  9. Distributeur selon la revendication 8, caractérisé en ce que les moyens de refoulement (4) sont commandés en fonction de la pression, notamment en fonction de la pression dans la chambre de pompe (51) de la deuxième pompe (6), la soupape de sortie (50) étant de préférence conçue comme soupape de surpression et réglée pour s'ouvrir au plus tard au début du refoulement de fluide.
  10. Distributeur selon une des revendications précédentes, caractérisé en ce qu'un apport d'air (52) est prévu pour un réservoir de stockage alimentant le distributeur (1) ,et il est de préférence raccordé à la chambre de pompe (51) des moyens de refoulement (4) par une soupape d'apport d'air (53) se fermant en fonction de la course.
EP91118296A 1990-11-09 1991-10-26 Distributeur de fluide Expired - Lifetime EP0484773B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4035688 1990-11-09
DE4035688A DE4035688A1 (de) 1990-11-09 1990-11-09 Austragvorrichtung fuer medien

Publications (2)

Publication Number Publication Date
EP0484773A1 EP0484773A1 (fr) 1992-05-13
EP0484773B1 true EP0484773B1 (fr) 1996-08-14

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EP91118296A Expired - Lifetime EP0484773B1 (fr) 1990-11-09 1991-10-26 Distributeur de fluide

Country Status (6)

Country Link
US (1) US5443185A (fr)
EP (1) EP0484773B1 (fr)
JP (1) JP2981327B2 (fr)
AT (1) ATE141190T1 (fr)
DE (2) DE4035688A1 (fr)
ES (1) ES2090206T3 (fr)

Families Citing this family (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CA2073256C (fr) * 1990-11-07 1999-01-26 Shoji Uehira Pompe pour la distribution de mousse
DE19711791A1 (de) * 1997-03-21 1998-09-24 Pfeiffer Erich Gmbh & Co Kg Austragvorrichtung für Medien
DE19723134A1 (de) * 1997-06-03 1998-12-10 Pfeiffer Erich Gmbh & Co Kg Austragvorrichtung für Medien
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Also Published As

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ATE141190T1 (de) 1996-08-15
ES2090206T3 (es) 1996-10-16
JPH0761485A (ja) 1995-03-07
DE4035688A1 (de) 1992-05-14
JP2981327B2 (ja) 1999-11-22
US5443185A (en) 1995-08-22
DE59108075D1 (de) 1996-09-19
EP0484773A1 (fr) 1992-05-13

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