EP0199143B1 - Pompe à piston coulissant pour délivrer des substances fluides - Google Patents

Pompe à piston coulissant pour délivrer des substances fluides Download PDF

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Publication number
EP0199143B1
EP0199143B1 EP86104327A EP86104327A EP0199143B1 EP 0199143 B1 EP0199143 B1 EP 0199143B1 EP 86104327 A EP86104327 A EP 86104327A EP 86104327 A EP86104327 A EP 86104327A EP 0199143 B1 EP0199143 B1 EP 0199143B1
Authority
EP
European Patent Office
Prior art keywords
piston
pump
thrust
pump according
spring
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
Application number
EP86104327A
Other languages
German (de)
English (en)
Other versions
EP0199143A1 (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
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 Ing Erich Pfeiffer GmbH filed Critical Ing Erich Pfeiffer GmbH
Publication of EP0199143A1 publication Critical patent/EP0199143A1/fr
Application granted granted Critical
Publication of EP0199143B1 publication Critical patent/EP0199143B1/fr
Expired 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
    • B05B11/1023—Piston pumps having an outlet valve opened by deformation or displacement of the piston relative to its actuating stem
    • B05B11/1026—Piston pumps having an outlet valve opened by deformation or displacement of the piston relative to its actuating stem the piston being deformable and its deformation allowing opening of the outlet
    • 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
    • B05B11/1042—Components or details
    • B05B11/1073—Springs
    • B05B11/1077—Springs characterised by a particular shape or material

Definitions

  • the invention relates to a manually operated thrust piston pump for dispensing flowable media with a piston unit displaceable in a cylinder against a return spring, the pump piston of which lies approximately in the pump axis and delimits a pump chamber with the cylinder in which the return spring lies.
  • a thrust piston pump of this type has become known, in which the return spring is formed in the form of a metallic helical compression spring by a separate and separately to be assembled component. This can result in a spring characteristic that is not desirable in every case or for every medium.
  • the invention is based on the object of creating a thrust piston pump of the type mentioned, which ensures a particularly simple construction and an uncomplicated assembly of the return spring despite the smooth operation of this return spring.
  • the return spring is formed by at least one rod-shaped spiral spring and forms a component with the piston unit.
  • a spring characteristic that is particularly advantageous for many applications can be achieved.
  • the spiral spring lying completely within the envelope surface of the cylinder or the piston raceway works due to the design according to the invention within the medium to be pumped, which acts differently on the spring deformation of a spiral spring than on those of a helical compression spring. If the spiral spring is slidably supported within the pump chamber, there is also the advantage of good lubrication of the surfaces sliding against one another by the medium to be pumped itself.
  • the spiral spring is guided on a sliding surface inclined to the pump axis, which is provided in particular directly after the piston race of the cylinder and is formed by an inner cone adjoining the piston race via an annular shoulder, so that the spiral spring itself, in the manner of a displacer who can participate in pumping. Due to the inclined sliding surfaces, an advantageous deflection of the spiral spring, which is directed radially inward with increasing spring deformation, is achieved, and moreover, by choosing the angular position of the sliding surface, the force vector of the restoring force can be determined with the same configuration of the spiral spring.
  • the spiral spring has a plurality of freely projecting spring arms distributed around the pump axis, which preferably diverge towards their free ends in the relaxed state and / or in the pretensioned initial position, the spiral springs in particular in the relaxed state and / or in the initial position of the piston unit are approximately rectilinear and diverge at an acute angle.
  • a particularly advantageous further development consists in that, adjacent to the deflection side of the bending window, a counter member is provided for this, which is located adjacent to the end of the bending spring arranged on the piston unit and is preferably formed by a common central punch for all bending springs.
  • the manufacture of the thrust piston pump can be simplified even further in that the spiral spring forms a one-piece component with the piston rod of the piston unit and its inner end and consists of plastic.
  • the piston sleeve of the pump piston can be made from a different material than the spiral spring.
  • a further advantageous embodiment consists in that the spiral spring lies at least partially within a sleeve-shaped piston sleeve of the pump piston, the radial spring of the spiral spring adjoining an outlet valve seat for a valve body which is integrated with the piston sleeve and which is axially displaceable relative to the piston rod. This results in very compact dimensions even in the longitudinal direction of the piston unit.
  • a thrust piston pump with a piston unit displaceable in a cylinder, in particular of the type described, that the piston rod between its outer end and a support surface has an approximately clear cross section of the piston sleeve at least on the outer circumference of the support surface in the direction thereof has expanded and up to the support surface expanding and assembly sliding section for the piston sleeve.
  • the pump piston of the piston unit which is located approximately in the pump axis and surrounds the piston rod, is formed, for example, by a sleeve-shaped, elastic piston sleeve biased axially between the rear support surface and the front valve seat of the outlet valve, so that the distance between the support surface and the Valve seat, for example by one-piece design of the piston rod, is precisely defined before assembly of the piston sleeve, and the axially resilient preload of the piston sleeve is precisely determined after assembly.
  • the piston sleeve can be assembled using a very simple method, namely from the outer end of the piston rod, after which the piston sleeve is automatically widened by moving towards the support surface on the expansion-sliding section so that it when the support surface overflows it springs back under a resilient constriction and then rests against the support surface in a locked manner.
  • the assembly sliding section adjoining the outer tapered end and / or the assembly sliding section adjoining the inner expanded end of the expanding sliding section can be essentially continuously cylindrical.
  • the expansion-sliding section is expediently provided at a distance from the outer end of the piston rod or approximately in the middle between the outer end and the support surface, it preferably forming a stop shoulder for a discharge head to be plugged onto the outer end section of the piston rod, so that its relative Axial position is precisely defined.
  • the piston sleeve is axially compressed at least so far from its end associated with the support surface that it has the prestress corresponding to its prestressed mounting position; however, it is also conceivable to compress the piston sleeve even further here and, after passing over the support surface and springing back axially, also spring back in the axial direction.
  • the support surface and the valve seat of the piston rod are formed by a one-piece component, the piston rod preferably being formed in one piece throughout.
  • a thrust piston pump with a cylinder housing which has a cylinder cover that closes its outer end and a flange flange, in particular with this protruding flange edge, with an annular seal for the sealed attachment to the opening limitation of an active substance vessel, the annular seal being integral with the Flange edge is designed to attach the pump.
  • a ring seal formed by a separate, enclosed component this results in a very secure sealing engagement of the ring seal with a simple design and considerably simplified installation, so that this design is particularly suitable for thrust piston pumps which can be arranged detachably on refillable vessels.
  • the ring seal can be made very compact, space-saving and hygienic, since there is a significantly reduced number of mutually adjacent sealing surfaces and thus sealing gaps.
  • a particularly high and also adjustable sealing effect results if the ring seal protrudes over the inner end face of the flange rim and has an acute-angled conical sealing surface, the sealing surface of the ring seal adjoining an annular shoulder of the flange rim and having a larger width than the width of the vessel opening .
  • the thrust piston pump 1 has a two-part pump housing 2 and a piston unit 3 lying in its pump axis 4, which can be moved back and forth in the direction of the pump axis 4.
  • the pump housing 2 consists essentially of two components.
  • the one component which is reduced several times to the inner end, forms a cylinder 5, while the other component is a sleeve-shaped cylinder cover 6 which, apart from the end face, also has the outer open end of the other component on the inner circumference and on the outer circumference, each with sleeve-shaped concentric to one another Approaches 7, 8 overlaps.
  • a hose 10 or the like is to be inserted as an intake duct, the lower end of which is to be arranged in the bottom region of a vessel 11 indicated by dash-dotted lines in FIG. 1, in the vessel neck 12 of which the pump 1 is sealed is attached.
  • the piston unit 3 has a piston rod 13, which is composed of two rod parts 14, 15 which are essentially arranged one behind the other and have their mutually facing ends, and which delimits, for example, a central outlet channel 16.
  • the piston rod 13 passing through the inner shoulder 7 of the cylinder cover 6 carries, within the pump housing 2, a sleeve-shaped piston sleeve 17 lying in the pump axis 4, which on the inner part of its length has a sleeve-shaped piston lip 18 which is expanded in the shape of a truncated cone to its free end and decreases in wall thickness and forms a sleeve-shaped piston neck 19 with an approximately constant wall thickness at the outer end section.
  • the piston sleeve-shaped transition area between the piston lip 18 and the piston Neck 19 forms the piston sleeve 17 by means of an annular bead projection provided on its inner circumference, a valve body 21 of an outlet valve 20 which, in the closed position according to FIG. 2, bears against an annular valve seat 22 of the piston rod 24.
  • the inwardly frusto-conical valve seat 22 is formed by an annular shoulder of a rod head 23 which is provided at the inner end of the piston rod 13 and has a larger diameter than the inner diameter of the piston sleeve 17 in the region of the valve body 21 and is at least partially inside the piston lip 18 .
  • the diameter of the portion of the piston rod 13 or of the rod part 15 which adjoins the rod head 23 to the outside is at most as large as the outside diameter as the inside diameter of the relaxed piston neck 19 or slightly smaller.
  • the outer end of the piston sleeve 17 or the piston neck 19 is supported with its associated end face on an annular shoulder-shaped support surface 24 of the piston rod 13 with axial prestressing, such that the piston neck 19 passes through the valve seat 22 and the support surface 24 when the piston sleeve 17 is braced Compression is resiliently biased in the axial direction and, for example, is slightly bulged according to FIG. 2.
  • the support surface 24 is formed in the illustrated embodiment by the inner end surface of the outer rod part 14, which coaxially surrounds the outer end portion of the inner rod part 15.
  • the inner end of the inner shoulder 7 of the cylinder cover 6 forms stops cooperating with the piston sleeve 17 for fixing the starting position of the piston unit 3.
  • the piston sleeve 17 has in the area of the transition between the piston lip 18 and the piston neck 19, that is to say approximately in the axial area of the valve body 21, on the outer circumference a truncated cone-shaped inward sealing and stop surface 25, which in the initial position of the piston unit 3 under the restoring force acting thereon on the inner boundary edge of the through opening 26 formed by the cylinder cover 6 for the piston unit 3 or the piston rod 13 abuts and thereby seals the associated space of the pump housing 2 to the outside; at the same time, this causes a stretching force on the piston sleeve 17, under which this is additionally pressed against the valve seat 22 for its own resilience.
  • the cylinder 5 forms on the inner circumference at least over the maximum stroke of the piston lip 18 or the pump piston 28 formed thereby, the cylindrical piston raceway 27.
  • the piston raceway 27 merges via an inner annular shoulder 29 into an inner cone 30 converging at an acute angle, which is formed by a continuation of the component of the pump housing 2 forming the cylinder 5.
  • an intake valve 31 in the form of, for example, a ball check valve is located in the intake path of the pump immediately adjacent to the end section 9.
  • the cylinder 5 and the inner cone 30 delimit a pump chamber 32, in which a spiral spring 33 is located as the return spring for the piston unit 3.
  • the spiral spring 33 is formed in one piece with the rod head 23 and has a plurality of spring arms 34 which are evenly distributed around the pump axis 4 and which project freely in the direction of the intake duct and diverge at an acute angle in axial direction in this direction.
  • the free ends 35 of the spring arms 34 bear against the sliding surface 36 which is inclined to the pump axis 4 and which is formed by the inner cone 30; the spring arms 34 can be designed so that they are approximately rectilinear in this state.
  • the spring arms 34 slide with increasing preload along the sliding surface 36 until their free ends 35 are at a short distance from the suction valve 31 at the end of the pump stroke and have reached their greatest pretension. The deflection of the spring arms 35 thus takes place radially inwards to the pump axis 4.
  • a counter member 38 Adjacent to the deflection side of the spring arms 34 determined thereby, a counter member 38 is provided at the inner end of the piston rod 13, which is formed by a central punch 39, common to all spring arms 34 and located in the pump axis 4, the circumferential surface of which in axial section is acute-angled into the radially inner boundary surfaces the spring arms 35 merges.
  • This counter member 38 results in an increased rigidity of the spring arms 34 and a reduction in the free volume of the pump chamber 32 at the end of the pump stroke.
  • the spring arms 34 lie partially inside the piston sleeve 18, so that a very space-saving and compact design results.
  • the radially outer surfaces 40 of the spring arms 34 facing away from the pump axis 4 directly adjoin the outer circumference of the valve seat 22.
  • the outlet channel 16 of the piston rod 13 ends like a blind hole in the area of the rod head 23 and is connected via transverse channels 41 to that cylinder-jacket-shaped space which lies between the valve seat 22 and the support surface 24 within the piston sleeve 17.
  • the piston lip 18 runs onto the annular shoulder 29 according to FIG. 4, after which the piston rod 13 can be pushed further into the pump housing 2 by a predetermined opening distance until it reaches an associated stop position. 4 is lifted off the valve seat 22 and thereby the outlet valve 20 is opened, so that the medium located under pressure in the pump chamber 32 when the suction valve 31 is closed abruptly through the outlet valve 20, the transverse channels 41 and can escape the outlet channel 16.
  • a discharge head 42 for manual operation of the pump is placed on the outer end of the piston rod 13, for example, which has the outlet mouth of the pump, not shown.
  • the pump is particularly suitable for metering, atomizing and the like. The medium to be dispensed.
  • the piston neck 19 is axially resiliently stretched with further bulging.
  • a restoring force acts on it, which is generated not only by the spiral spring 33 at the beginning of the return stroke, but also by the piston neck 19 until the outlet valve 20 closes.
  • the spiral spring 33 completely returns the piston unit 3 to its initial position according to FIG. 2.
  • FIGS. 5 to 7 parts that correspond to one another have the same reference numerals as in FIGS. 1 to 4, but in FIG. 5 with the index “a ” , in FIG. 6 with the index “b” and in FIG. 7 with the index «c» is used.
  • the piston rod 13a of the piston unit 3a is formed in one piece throughout its length, so that the entire piston unit 3a consists of only two components, namely the piston rod 13a and the piston sleeve 17a, with the piston rod 13a simultaneously the return spring of the pump is made in one piece.
  • the rod head 23a has no central punch within the spring arms 34a of the spiral spring 33a.
  • the spring arms 34a can also be approximately straight in the completely relaxed state; they are expediently tapered uniformly at an acute angle to their free ends 35a.
  • the piston rod 13a has between its outer end 43 and the support surface 24a has an expansion-sliding section 44 which is approximately expanded from the clear cross-section of the piston sleeve 17a to the outer circumference of the support surface 24a and which lies on the outer circumference of the piston rod 13a between two mounting sliding sections 45, 46, which have a constant width over their length, preferably cylindrical are.
  • the expanding sliding section 44 is formed by a peripheral section which is widened at an acute angle in the shape of a truncated cone from the smaller outer diameter of the outer mounting sliding section 45 reaching to the end 43 to the larger diameter of the inner mounting sliding section 46, which has the same diameter as the support surface 24a Has outer circumference and continuously extends up to this.
  • the outer diameter of the outer assembly sliding section 45 is expediently at most as large as the clear width of the completely relaxed piston sleeve 17a or of its piston neck 19a.
  • the piston sleeve 17a is inserted from the outer end 43 onto the piston rod 13a and pushed over the expansion-sliding section 44, wherein it is expanded in a resilient manner.
  • the valve body 21a has reached the valve seat 22a
  • the free end of the piston neck 19a is still in the region of the assembly sliding section 46.
  • the piston neck 19a is axially resiliently compressed from its outer end surface associated with the support surface 24a until the outer end of the piston neck 19a has overflowed the supporting surface 24a and, with a resilient radial narrowing, jumps into its mounting position associated with the supporting surface 24a, in which the axial preload of the piston sleeve 17a is maintained in a precisely predetermined size.
  • the widening of the outer end of the piston neck 19a can take place in such a way that the piston neck 19a is adjacent to the support surface 24a even with a radially inward bias against the portion of the piston rod 13a adjoining the inner circumference of the support surface 24a.
  • the widening-sliding section 44 which can also be used with a two-part design of the piston rod according to FIGS. 2 and 4, is, as these figures show, at the same time expediently provided as a stop shoulder for the discharge head 42 to be plugged onto the outer end section of the piston rod 13, so that the axial position of the discharge head 42 relative to the piston rod 13 is precisely defined by this stop shoulder.
  • the expansion-sliding section 44 expediently begins approximately in the middle of the length between the outer end 43 and the support surface 24a.
  • the expansion sliding section 44b can also extend approximately to the support surface 24b, so that the inner mounting sliding section 46 according to FIG. 5 is omitted and the expansion of the piston sleeve extends over a larger axial displacement path with respect to the piston rod 13b .
  • the support surface 24b can be formed by a recessed annular front shoulder, which is delimited on the outer circumference by a collar 47 projecting over it, which can be formed by a closed annular collar or individual cams distributed over the circumference.
  • the outer circumference of the collar 47 expediently forms a continuous continuation of the widening sliding section 44b or, in the case of the embodiment according to FIG. 5, of the mounting sliding section extending as far as the supporting surface.
  • the associated end of the piston neck of the piston sleeve is positively secured against expansion by the collar 47.
  • this can have an inner collar 48 with an enlarged diameter following the inner circumference of the support surface 24b, on which the outer end of the piston neck after assembly with it Sealed inner circumferential surface.
  • the pump housing 2 has an annular flange edge 49 projecting beyond its outer circumference on, which is provided for the abutment of the pumps on the outer end face of the vessel neck 12 and is formed in one piece with a component of the pump housing 2, in the exemplary embodiment shown with the cylinder cover 6.
  • the flange edge lies at the inner end of the outer sleeve-shaped extension 8 of the cylinder cover 6 and projects beyond its outer circumference.
  • annular seal 50 is provided which is formed in one piece with the flange rim 49 and thus with the cylinder cover 6.
  • the ring seal 50 projects axially inward beyond the ring shoulder 51, which is formed by the inner end face of the flange rim 49 and is intended to bear against the end face of the neck 12 of the vessel.
  • the sealing surface 52 formed by the outer circumference of the ring seal 50 is tapered in the shape of a truncated cone to its inner end and, following the ring shoulder 51, has its greatest width, which is slightly larger than the width of the opening of the vessel neck 12.
  • the ring seal 50 is exposed on the preferably cylindrical inner circumference, i.e. with a radial distance from the adjacent outer circumference of the pump housing 2 so that it can spring radially inwards without deformation of the pump housing.
  • a fastening cap 53 is used to fasten the thrust piston pump 1 to the vessel 11, which, for example as a screw cap, overlaps the vessel neck 12 on the outer circumference and rests with an inner shoulder on the outer annular end face of the flange rim 49 such that it is clamped against the end face of the vessel neck 12 and the Ring seal 52 engages in the vessel neck 12 under radial sealing pressure.
  • the fastening cap 53c can also be formed in one piece with a component of the pump housing 2c, in the exemplary embodiment shown with the cylinder cover 6c.
  • the end cap of the fastening cap 53c expediently forms the flange edge 49c, which in turn merges in one piece into the outer sleeve-shaped extension 8c of the cylinder 6c and into the ring seal 50c.
  • the design according to the invention makes it possible to produce thrust piston pumps which ensure very reliable operation with a very small number of components.
  • the entire piston rod and the return spring are formed by a single one-piece component; the cylinder housing or its cylinder cover can be combined with the fastening cap, the flange edge and the vessel seal to form one component.

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  • Reciprocating Pumps (AREA)
  • Details Of Reciprocating Pumps (AREA)

Claims (12)

1. Pompe à piston de poussée à manoeuvre manuelle pour l'émission de milieux fluides avec une unité de piston (3) déplaçable dans un cylindre (5) contre un ressort de rappel, dont le piston de pompage (28) situé sensiblement dans l'axe de la pompe (4) délimite avec le cylindre (5) une chambre de pompe (32) dans laquelle se trouve le ressort de rappel, caractérisée en ce que le ressort de rappel est constitué par au moins un ressort de flexion (33) et constitue un élément fonctionnel avec l'unité de piston (3).
2. Pompe à piston de poussée selon la revendication 1, caractérisée en ce que le ressort de flexion (33) est guidée sur une surface de glissement (36) oblique par rapport à l'axe de la pompe (4), qui, en particulier, est prévue avec un raccordement direct à la voie de déplacement (27) du cylindre (5) et est constituée par un cône intérieur (30) se raccordant au moyen d'un épaulement annulaire (29) à la voie de déplacement du piston (27).
3. Pompe à piston de poussée selon la revendication 1 ou 2, caractérisée en ce que le ressort de flexion (33) présente plusieurs bras de ressorts (34) répartis autour de l'axe de la pompe (4), qui font saillie librement et qui, de préférence, à l'état détendu et/ou en position initiale précontrainte, divergent en direction de leurs extrémités libres (35), les ressorts de flexion (33) étant, en particulier à l'état détendu et/ou en position initiale de l'unité de piston (3) sensiblement rectilignes et divergeant suivant un angle aigu.
4. Pompe à piston de poussée selon l'une des revendications qui précédent caractérisée en ce qu'il est prévu pour le ressort de flexion (33) un contre- élément (38) voisin du côté de la déviation du ressort de flexion (33), qui est voisin de l'extrémité du ressort de flexion (33) disposée sur l'unité de piston (3) et qui est constitué de préférence par un tampon central (39) commun pour tous les ressorts de flexion (33).
5. Pompe à piston de poussée selon l'une des revendications qui précédent, caractérisée en ce que le ressort de flexion (33) constitue un élément fonctionnel d'une seule pièce avec la tige de piston (13) de l'unité de piston (3) et son extrémité intérieure, et est constitué en matière plastique.
6. Pompe à piston de poussée selon l'une des revendications qui précédent, caractérisée en ce que le ressort de flexion (33) se trouve au moins en partie, à l'intérieur d'une garniture de piston (17) en forme de manchon du piston de pompage (28) et en ce que le ressort de flexion (33) se raccorde par sa surface extérieure (40) radiale à un siège de soupape de sortie (22) pour un corps de soupape (21) intégré avec la garniture de piston (17), qui est mobile axialement par rapport à la tige de piston (13).
7. Pompe à piston de poussée selon l'une des revendications 1 à 6, caractérisée en ce que la tige de piston (13a) présente entre son extrémité extérieure (43) et une surface d'appui (24a) une partie glissante d'élargissement et de montage (44, 45, 46) pour la garniture de piston (17a) s'étendant approximativement à partir de la section intérieure de la garniture de piston (17a), au moins sur le pourtour extérieur de la surface d'appui (24a) en direction de cette dernière élargie et jusqu'à la surface d'appui (24a).
8. Pompe à piston de poussée selon la revendication 7, caractérisée en ce que la partie de glissement-montage (45, 46) se raccordant à l'extrémité extérieure rétrécie et/ou à l'extrémité intérieure élargie de la partie de glissement-élargissement (45, 46) est prévue avec une forme essentiellement cylindrique continue et à quelque distance de l'extrémité extérieure (43) de la tige de piston (13a), approximativement à une même distance de l'extrémité extérieure (43) et de la surface d'appui (24a) et constitue un épaulement de butée pour une tête de décharge (42) à enfoncer sur la partie d'extrémité extérieure de la tige de piston (13a).
9. Pompe à piston de poussée selon la revendication 7 ou 8, caractérisée en ce que la surface d'appui (24a) et le siège de soupape (22a) de la tige de piston (13a) sont constitués par un bloc fonctionnel d'une seule pièce, la tige de piston (13a) étant, de préférence, constituée d'une seule pièce continue.
10. Pompe à piston de poussée selon l'une des revendications 1 à 9, caractérisée en ce qu'un joint d'étanchéité annulaire (50) est constitué d'une seule pièce avec un rebord (49) pour la fixation de la pompe.
11. Pompe à piston de poussée selon la revendication 10, caractérisée en ce que le joint d'étanchéité annulaire (49) fait saillie sur la face frontale du rebord 49 et présente une surface de contact (52) en forme de tronc de cône à angle aigu, laquelle surface de contact (52) du joint d'étanchéité annulaire (50) se raccorde à un épaulement annulaire (51) du rebord (49) et à une largeur maximale qui est supérieure à la largeur de l'ouverture du récipient.
12. Pompe à piston de poussée selon l'une des revendications qui précède, caractérisée en ce que le joint d'étanchéité annulaire (50c) est constitué d'une seule pièce avec un capuchon de fixation (53c) de la pompe (10) sur lequel le paroi frontale du couvercle de cylindre (60) constituant le rebord (49c) fait saillie vers l'extérieur et le joint d'étanchéité annulaire (50c) fait saillie vers l'intérieur.
EP86104327A 1985-04-24 1986-03-27 Pompe à piston coulissant pour délivrer des substances fluides Expired EP0199143B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3514719 1985-04-24
DE19853514719 DE3514719A1 (de) 1985-04-24 1985-04-24 Schubkolbenpumpe zur ausgabe von medien

Publications (2)

Publication Number Publication Date
EP0199143A1 EP0199143A1 (fr) 1986-10-29
EP0199143B1 true EP0199143B1 (fr) 1989-06-14

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP86104327A Expired EP0199143B1 (fr) 1985-04-24 1986-03-27 Pompe à piston coulissant pour délivrer des substances fluides

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US (1) US4762475A (fr)
EP (1) EP0199143B1 (fr)
JP (1) JPS61247884A (fr)
DE (2) DE3514719A1 (fr)

Families Citing this family (32)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4953758A (en) * 1988-10-24 1990-09-04 Mark-O Industries Valve construction
FR2656901B1 (fr) * 1990-01-08 1993-02-19 Step Soc Tech Pulverisation Perfectionnement d'une pompe-doseuse a precompression pour en ameliorer l'amorcage et garantir sa simplicite d'assemblage.
DE4005529A1 (de) * 1990-02-22 1991-08-29 Pfeiffer Erich Gmbh & Co Kg Austragkopf fuer medien
DE4110303A1 (de) * 1991-03-28 1992-10-01 Pfeiffer Erich Gmbh & Co Kg Austragvorrichtung fuer medien
US5282552A (en) * 1991-05-20 1994-02-01 Hygiene-Technik Inc. Disposable plastic liquid pump
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Also Published As

Publication number Publication date
DE3514719A1 (de) 1986-10-30
US4762475A (en) 1988-08-09
JPS61247884A (ja) 1986-11-05
DE3663937D1 (en) 1989-07-20
EP0199143A1 (fr) 1986-10-29

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