EP0792192A1

EP0792192A1 - Media dispenser

Info

Publication number: EP0792192A1
Application number: EP95939254A
Authority: EP
Inventors: Karl-Heinz Fuchs
Original assignee: Caideil MP Teoranta
Current assignee: Caideil MP Teoranta
Priority date: 1994-11-19
Filing date: 1995-11-10
Publication date: 1997-09-03
Anticipated expiration: 2015-11-10
Also published as: DE4441263A1; AU4115596A; ES2203648T3; DE59510772D1; KR100327289B1; JP3935204B2; BR9510339A; JPH10513101A; WO1996015855A1; KR970706908A; US6073814A; AU703646B2; EP0792192B1; ATE247526T1

Abstract

PCT No. PCT/EP95/04426 Sec. 371 Date Apr. 11, 1996 Sec. 102(e) Date Apr. 11, 1996 PCT Filed Nov. 10, 1995 PCT Pub. No. WO96/15855 PCT Pub. Date May 30, 1996A discharge apparatus (1) comprises within the pump housing (2) an integral full-length working member (10) having spring sections (28, 29, 30) and sections located between these which form a valve housing (18), fastening members for connecting to a piston (12) and the like. The spring section in each case may be configured as a helical or torsion spring having a closed spring jacket, thus resulting in simple manufacture and simple assembly with high functional reliability.

Description

description

Austraσvorrichtunσ for media

The invention relates to a discharge device for flowable and / or other media, which e.g. can be gaseous, liquid, pasty and / or powdery before or during the discharge process. Only a single media component or separate components can be discharged at the same time or in such a way that their start and / or discharge is delayed relative to one another.

According to the invention, the discharge device has at least one working member, such as a resilient element, in one piece

Working spring or the like, which is at work, e.g. the discharge work, the device is tensioned and relaxed and / or can perform other functions. Such functions can be control movements, resetting movements, closing movements, stop functions, sliding guides or the like. The discharge device or the respective working member is expediently made exclusively of plastic or non-metallic materials, which can be copolymers, such as polyethylene, polypropylene or other thermoplastics, so that the respective component can be produced as a molded part.

Furthermore, the discharge device, which can be gripped with one hand, carried freely and actuated at the same time, should discharge or atomize the medium over most of its actuation path, in particular immediately after at least partially closing an inlet. The lowest tension of the spring in the initial and resting state of the Discharge device is advantageously above 2 to 5 N and below 10 or 8 N, the tension at the start of the discharge or when the inlet closes, above 10 or 15 N and below 30 or 25 N and the highest tension at the end of the discharge process 40 or 50 N and below 100 or 80 N. The discharge device can be made very small, namely, with regard to the surfaces that come into contact with the media, have a maximum width of 30, 20 or approximately 10 mm, while their length is at most 50 or 40 mm. This length relates, for example, to the distance between the inner bottom of a pressure chamber and the outer end of an actuating handle in a discharge device which is to be inserted into a small vial with the inner end through the neck of the vessel. The discharge device is suitable for very small discharge volumes for each complete, stroke-limited discharge process, namely

Volumes below one, half or three tenths of a centimeter or milliliter. The manual actuating force for a discharge process can then be below 200 or 100 N.

The invention is also based on the object of providing a discharge device for media, in which

Disadvantages of known training avoided and / or advantages and effects of the type described can be achieved. In particular, simple manufacture and / or fully automatic assembly and / or a very small number of components or a high level of functional reliability should also be ensured, even at different temperatures.

The respective working spring can have working sections which are expediently lined up in the longitudinal direction and have different stiffness or spring hardness per unit length. The respective working section can be a resiliently deformable spring section, a non-resilient intermediate section, a non-resilient end section and / or a resilient be the end section. The respective non-resilient section is expediently not brought about by spring coils placed closely or in contact with one another, but by a corresponding change in cross-section or other stiffening configurations of the working spring, so that the respective spring section over its entire length and up to one or both ends per unit length or spring winding can have essentially the same spring action. The respective spring turn advantageously forms full cross sections which have greatly different extents in directions lying opposite one another, for example a cross-sectional extension which is several times greater in the longitudinal direction of the spring than at right angles thereto or transverse or radial to the spring axis.

The respective working section can be designed as a completely closed or multiple or uniformly perforated hollow jacket, so that adjacent spring sections or spring windings are connected directly to one another not only via the gradient course but also in a bellows-like manner in the longitudinal direction of the spring. The connecting sections are movable with respect to one another in the longitudinal direction of the spring and can similarly connect adjacent truncated cones in longitudinal section at an angle of at most 90 ° or at acute angles or merge into one another in one piece.

It is particularly advantageous if the spring is subjected to torsion over its spring travel and thus torsional restoring forces are built up. These can then supplement the axial restoring forces, so that a relatively weakly dimensioned spring also produces high spring forces or a relatively linear spring characteristic. The respective working section can be profiled on the inner and / or outer circumference in the manner of a one-, two- or multi-start thread as a helix or high helix. Are the inner ones and outer spiral sections are approximately congruent, the wall thickness of the working section is approximately constant in this area over the circumference or the axial extent. The respective outer or inner helix can be interrupted or go through without interruption over at least two to all working sections with approximately the same diameter or pitch, so that very simple manufacture is possible.

The helix angle of the helix can be between 10 ° and 60 °, in particular 20 ° and 45 °, the minimum or

Maximum value in addition to these values 5 °, 30 °, 40 ° and 50 ° can be advantageous. If the spring is deformed such that adjacent turns sections of approximately the same diameter abut one another, a correspondingly lower internal material deformation or bend results in the case of multi-course design with turns of a plurality of helixes lying alternately one inside the other. The resilient torsional load can be increased by increasing the helix pitch. As a result, the spring tension remains even under high mechanical and thermal loads, e.g. up to at least 70 ° C.

The stiffened working section can then e.g. only be formed in that it only has radially outside of the inner cross-sections other than one or two adjacent spring sections, for example larger full cross-sections in the longitudinal and / or radial direction. The stiffened section can be axially and / or radially resilient, e.g. be resilient or essentially dimensionally rigid by cross-sectional crushing.

The inner and / or outer circumference of the respective working section is for sliding guidance on corresponding counter surfaces suitable to which it can only rest in a linear or cutting shape or over a larger axial extent. Furthermore, the respective circumference is suitable for media guidance, and it can form with the counter surface an approximately closed spiral channel over the circumference of its cross section. The directions of flow on the inner and outer circumference are advantageously directed in opposite directions, it being possible for the flow of the continuous flow to be reversed in the region of an end or a wall breakthrough of the working member. The respective spiral channel or the spiral groove could essentially close completely via the spring travel up to the end of the spring travel, but the dimensions are expediently provided such that the spiral channel or the cavity of the working component always remains open.

Each of the working sections can also form a form-locking member, a stop member, a centering member, an anti-rotation device or the like for its axial, radial and / or non-rotatable position securing device or that of the working spring. Such or stiffened working sections can be considerably shorter in the longitudinal direction of the spring than at least one or all spring sections or the spring section or the immediately following one. The respective spring section, in turn, can have a greater or a smaller length compared to its outer and / or inner width, depending on the spring travel or spring action required. If the working spring is fixed with a fastening section by means of a snap connection or the like axially and / or radially essentially free of play with respect to another component, such as a displacement piston, then the two subsequent spring sections can work completely independently of one another. In the case of a stop section, the effective spring length is shortened or the spring characteristic increases abruptly after the stop position is reached, so that, for example, it closes of an inlet valve requires a lower actuation force and then an increased actuation force. In contrast, in the return movement, both spring sections lying on both sides of the stop section can be effective from the start.

The design according to the invention is particularly suitable for piston or thrust piston pumps, which e.g. have a pressure-dependent outlet valve, which lies within the piston and has a valve closing body separate from the piston, which executes axial working movements with respect to the piston. The valve body is expediently formed in one piece with the adjoining spring section or with the associated valve spring or two to all working sections of the associated working spring. If the pump is designed as a self-priming pump, it has an inlet valve which keeps the pressure or displacement chamber at the inlet closed in a pressure-tight manner during the pumping stroke. The valve can be designed as a stop-limited valve and / or as a slide valve. Its axially movable valve body can be formed in one piece with each of the other working sections of the working member mentioned.

The discharge device can also be designed such that its pump chamber is not to be refilled by self-suction or return stroke movements, but instead contains the entire media supply of the discharge device from the outset. Each of the working sections or its inner and / or outer circumference can be partially or completely outside the media-carrying areas, for example on the outside of the pump chamber, so that it never comes into contact with the medium. The discharge device or its components, such as the working spring or its individual working sections, can be manufactured and assembled very easily, in particular if the components are essentially rotationally symmetrical and are designed such that certain components contribute to the direct mutual engagement mutually longitudinal assembly movements have a self-centering effect on one another and come into the functional mutual engagement solely by longitudinal forces. This means that pre-assembly of modules can be dispensed with. For example, the working spring and the piston can be lowered one after the other in both possible sequences under the force of weight in the longitudinal direction into a pump housing, after which the positional lock between the piston and the working spring automatically engages by applying an axial force. The piston can then form the only separate front closure of the housing, or a separate housing cover can be attached for this purpose, via which the mentioned axial assembly force can also be applied. Such a cover, which also snaps into the housing in a self-centering manner, can be provided at the inner and / or outer end of the pump housing. The inner end is that end which is remote from the outer end, this outer end being closer to the manual discharge operation or the media outlet. If the inner end is connected to the respectively associated outer end, this connection direction usually corresponds approximately to the discharge flow direction in a main section of the outlet channel or the pump chamber, this flow direction being opposite to the pump movement of the displacement piston.

These and further features emerge from the description and the drawings in addition to the claims, the individual features each individually or in the form of subcombinations in one embodiment of the invention and in other fields and can represent advantageous and protectable designs for which protection is claimed here.

Exemplary embodiments of the invention are shown in the drawings and are explained in more detail below. The drawings show:

1 is a discharge device according to the invention, partly in axial section,

2 shows the discharge device according to FIG. 1 in an enlarged and slightly modified design,

3 shows a section of a further embodiment in axial section,

4 shows a section of a further embodiment of a housing and

5 shows a further embodiment of a discharge device, partly in axial section.

The discharge device 1 has a base body 2 which is to be arranged in a fixed position with respect to a media store indicated by dash-dotted lines and which is provided for filling or flow through with the medium. The housing-shaped base body 2 is composed of an elongated, sleeve-shaped housing part 3 and a cover 4, which closes the outer end of the cup-shaped housing part 3 in an annular manner and is penetrated by a discharge actuation 5. At its outer end, the discharge actuation 5 carries a head 6, the outermost end face of which forms a pressure handle 7 and which has a radially directed media outlet 8 in the form of an atomizing nozzle opening into the open. The head 6 is fastened to the outer end of a piston unit 9 by axial plugging and can be moved synchronously with this piston unit 9 relative to the base body 2 against its inner end or against its outer end.

Essentially completely encased and covered on the outside on the end face, an elongated working unit or working spring 10 is sunk inside the component 3 or 4, which in the initial state extends approximately over the entire inner length of the part 3. Arbitrary pairs of the arrangements 2 to 10 can be axially parallel or axially parallel to one another and thereby determine a central central axis 11 of the discharge device 1. At the inner end, the piston unit 9 forms a cup-shaped piston 12, which at the outer end has an annular bottom wall a plunger 13 goes over. This plunger 13 passes through the cover 4 to the outside and carries the head 6. Each of the components 3, 4, 9, 10 can be formed in one piece, so that the discharge device 1, without head 6 and possibly without suction - or filler pipe, can be assembled from only four components so that the medium can be pumped out through the plunger 13 through the pump chamber 14 of the basic housing 2.

The piston 12 runs with two axially spaced and oppositely projecting annular sealing lips sealed on the inner circumference of the casing of the housing 3, namely from a stop-limited starting position to a pump stroke end position in which the piston 12 itself does not strike. The piston 12 delimits the pump chamber 14 on its outer end face and, with its cavity, itself forms a longitudinal section of the volume-variable pump chamber 14. Component 9 or 12 or 13 can be locked against rotation with respect to component 2 or 3 or 4 in any stroke position in a positive or frictional manner.

Relative to the inner and / or outer piston lip of the piston 12, an outlet valve 15 is provided inside the piston unit 9 in the region of the bottom wall of the piston 12 which is integrally connected to the tappet 13 and which is above a limit pressure in the pumping chamber 14 opens automatically against restoring forces in that a valve body 16 lifts off a valve seat. The valve seat is formed by an annular inner shoulder, formed in one piece with the components 9, 12, 13 and forms an end stop for the closed position of the valve body 16, the closing movement of which towards the outer end of the discharge device 1 or parallel to the direction of flow of the medium in the valve 15 is directed.

At a respective distance from and between the inner and outer ends of the unit 2 or 3, an inlet valve 17 with two interacting valve parts, namely an axially movable valve body 18 and a valve seat 19 fixed to the housing, is provided within the housing 3. The inner end of the discharge device 1 or of the base body 2 is designated by 20 and the outer end by 21, which is formed by the outer end face of the head 6 when the discharge device is completely assembled. Each of the components mentioned or each longitudinal section of such a component has corresponding inner and outer ends, the inner end 20 being able to lie inside the media store, while the outer ends of the components 3, 4, 9, 10 are outside the media store. In the closed state, the inlet valve 17 separates an inlet chamber 22 in a pressure-tight manner from the pump chamber 14, which, when the valve 17 is open, connects with the chamber 22 is connected by direct connection of the two adjoining chamber ends. The inlet chamber 22 is essentially delimited exclusively by the housing 3, and an inlet channel 23 opens into it via an inlet opening 24, no further valve being provided between the media inlet of the inlet channel 23 and the inlet opening 24 or the valve 17 .

The inlet channel 23 is essentially formed by a flexible, tubular riser pipe which projects beyond the inner end 20 such that its media inlet lies in the region of the bottom of the storage vessel. The riser pipe

25 is formed here by a component separate from component 3 or 4 and arranged in a fixed position in a holder 26 of component 3, but can also be formed in one piece with the named component. The tubular bracket

26 receives the outer end of the riser pipe 25 on the inner circumference via a plug-in connection and forms with its outer end the inlet opening 24, which can be offset axially outwards with respect to the valve 17 and axially inwards with respect to the piston 12 which is at rest. Like the pipe 26, the inlet opening 24 lies essentially completely within the working member 10, the pipe 26 projecting in one piece only from the inner end face of the bottom wall 27 of the base body, which forms the inner end 20.

The working spring 10 forms a plurality of working sections 28 to 34 which axially adjoin one another, with sections directly adjoining one another having different lengths, internal widths and / or external widths, and bending or shape stiffnesses opposite each other both in the radial direction and in the axial direction can. Here, the sections 28, 29, 30 are provided as axially resilient or length-adjustable spring sections. while the sections 31 to 34 are essentially dimensionally stable against axial pull or pressure. Sections 31, 32, 34 are intermediate sections of working spring 10, while section 33 forms the outer end section of working spring 10.

The inner end 35 of the working spring 10 is formed by the end section 30 and is supported directly in relation to the base body 2 such that it always assumes the same axial position with respect to the latter and / or is secured against rotation in a frictional or positive manner. The working spring 10 is essentially hollow over its entire length, namely with continuously approximately continuous internal cross sections, the cavity being closed in a pressure-tight manner at the outer end by the section 33.

The jacket of the working spring 10 is essentially impermeable to the medium over its entire length, so that only the end 35 forms a transfer opening for the medium from the interior of the working spring 10 to the inlet chamber 22. The inner circumference 36 or the outer circumference 37 of the working spring 10 deviates from the cylindrical shape in the region of each of the sections 28 to 34 and over its axial extent, although the outer circumference of the sections 31 to 34 can be partially or completely cylindrical. The inner circumference 36 is formed essentially over all sections 28 to 32 and 34 of a continuously constant structure, namely in the manner of a two-way pointed thread by helices 39, so that an inner mold can be easily removed from the working spring 10 after it has been produced. The outer circumference 37 is formed only in the area of the sections 28 to 30, but not in the area of the sections 31 to 34 by corresponding helices 40 of a two-start pointed thread, which lies opposite the internal thread in such a way that in its area the jacket 38 of the respective section 28, 29, 30 has an approximately constant wall thickness. The radially innermost edge 41 of the helix 39 or the like can slide centered in the area of the holder 26 on its outer circumference, like the radially outermost edges 42 of the outer helices 40 on the inner circumference of the housing 3 or the chamber 22 and / or the piston 12 can slide centered. The sections 29 and 31 to 33 lie completely within the piston 12, the outer end of the section 28 extends into the piston 12, the section 34, like the largest longitudinal part of the section 28, lies completely in the chamber 14 which is enlarged relative to the chamber 22 and the portion 30 is closed completely Ven¬ til 17 in the chamber 22, whereas it partially projects into the chamber 14 at geöffne¬ tem valve 17 ^'.

The component 10 is positively fixed in the longitudinal direction exclusively relative to the component 9, 12, 13, and only in the area of the sections 31, 32, which engage in the inner circumference of the piston 12 via a snap connection 49 and an end stop so that they are secured in both opposite axial directions and / or directions of rotation, essentially free of play, friction or positive locking. Sections 31, 32 protrude radially over the outer circumference of the sections 28, 29 adjoining on both sides, the outer circumference of section 31 forming a snap member for resilient engagement in a snap opening on the inner circumference of the piston skirt and with Ab¬ stood between the piston lips. The section 32, on the other hand, which is offset axially inward, lies against an inner shoulder of the piston 12 in such a way that it is positively locked against outward movements. Between the sections 31, 32 there is a centering section which is radially slightly reduced compared to both and which abuts the inner circumference of the piston skirt. Compared to the rigid sections 31, 32 all other sections 28, 29, 30, 33, 34 can be moved axially and / or radially, namely as a result of the working stroke, the return stroke or pressure changes in the chamber 14.

Between the attachment 43 or the sections 31, 32 and its outer end or bottom wall, the piston 12 forms with its interior a chamber 44 which is separated from the chamber 14 by throttle cross-sections and which is considerably smaller than this, in which the sections 29, 33 and the valve body 16 lie and from which the media outlet leads out of the chamber 14 through the valve 15. The chamber 44 is in constant line connection with the chamber 14 via the throttle cross-sections or through passages 45 distributed over the circumference, the passages 45 passing the outer circumference of the sections 31, 32 and being formed by axial grooves on the inner circumference of the piston 12.

Support abutments distributed over the circumference, which are expediently formed by projections such as ribs 46, are provided as abutments for axial or rotationally secured support and radially self-centering guidance of the inner end 35.

These are formed in one piece with the housing 3 and protrude from the inside of the base 27 or the shell of the chamber 22 in such a way that the medium flowing out of the inner end 35 between them deflects in the opposite direction into the chamber 22 and can flow to the outer periphery of sections 28 to 34. The outer circumference of the holder 26 delimits a spiral channel 47 with the inner circumference of the sections 28, 34, 30, the gradient and cross section of which changes with the working stroke. Accordingly, the inner circumference of the chamber 22 and possibly also the inner circumference of the chamber 14 or the piston 12 with the outer helix 40 of the section 30 or 28 or 29 delimit a corresponding outer one Spiral channel 48. The spiral channels 47, 48 are each provided with two gears, and the spiral channel 48 also changes its slope and its cross section or its volume with the changes in length of the associated section 28, 29, 30, possibly at least approximately to zero, if helically adjoining helical flanks abut each other at the end of the stroke. The specific deformation of each spring 28, 29, 30 is approximately constant over the entire length of its coil 40.

If the chambers 14, 22 and the interior of the working spring 10 are completely filled with medium, an inward-directed stroke movement of the piston unit 9 initially only leads to a shortening and torsional stress of the compression springs 28, 30, as a result of which the compression springs adjoining them on both sides Valve body 18 is taken against the valve seat 19 with slight rotation. The valve seat 19 is formed by an annular rib, against which the opposite end face of the valve body 18 abuts after a first partial travel of the stroke and thereby blocks the valve passage in a pressure-tight manner. The shortening of the spring 30 is thereby ended, and with the further stroke only the spring 28 is effective, the inner end of which is secured against rotation by the end 35 or the section 34. However, the valve body 18 could also work in the manner of a slide valve in that its outer circumference comes into sealing engagement with the inner circumference of the chamber 22 and is not limited by a stop, so that the spring 30 also has torsion over the entire stroke of the piston 12 - or is subject to changes in length.

After the valve 17 has been closed, the further stroke movement leads to an increase in pressure in the chamber 14 and to a reduction in the cavity of the working spring 10, so that medium from this cavity via the opening 24 and the channel 23 back into the reservoir is pressed while the pressure in the Chamber 14 acts on the section 33 provided as a differential piston, which carries the valve body 16 on its outer end face. As soon as this pressure has exceeded a limit value, the compression spring 29, which has been constant up to that point, yields with shortening and torsional deformation, so that the valve 15 opens and the medium is completely in the plunger

13 enclosed outlet channel flows into the head 6 or the outlet nozzle 8. The pump stroke is ended by the piston unit 9 or the head 6 abutting the base body 2, but outside the chamber 14, the valve 15 closing immediately with the valve spring 29 turning back. Due to the spiral channels 48 and their narrowing, the medium is set into a rotational flow during the discharge in the chambers 14, 44 and its flow is accelerated by displacement. The outer end of the respective section 28, 29, 30 can be secured against rotation by the adjoining section 31, 32 or 33 or 34, in particular with respect to the base body 2 or the piston 12.

If the handle 7 is now released, the piston 12 executes a first part of the return stroke, in which the chamber, by the spring 28 when the valve 17 is initially still closed

14 is evacuated, while the cavity of the working spring 10 is already sucked in through the channel 23 by enlargement. The valve 17 then opens by means of the spring 30, so that the medium is sucked out of the cavity and the chamber 22 abruptly into the chamber 14 until the piston 12 has reached its starting position. The opening 24 is offset from the outside of the valve passage of the valve 17. During this suction, the medium is again set in a rotational flow both within the cavity and in the chambers 22, 14, but its flow is slowed down. The section 28 is longer than the section 30 and acts as a return spring only on the piston 12 during the section 30 acts not only as a valve spring for the valve 17, but also as a return spring for the piston 12. The head 6 is fixed in position in the axial direction with the piston unit 9.

The cover 4 is connected to the housing 3 with an axially latching snap connection 49, the sleeve-shaped edge at the outer end of the housing 3 being encompassed by the cover 4 on both the inner and the outer circumference. The lid 4 is formed in one piece with a fastening member 50 for fastening the base body 2 or the entire device 1 to the memory. The fastening member 50 is a cap which surrounds the body 3 in the region of the chamber 14 on the outer circumference at a distance, which is offset inwards relative to the outer end of the body 3 and here has an internal thread for engagement with an external thread on the neck of the accumulator. points. The cover 4 is also formed in one piece with a sleeve-shaped seal 51 which surrounds the body 3 on the outer circumference with a gap distance and the outer circumference of which is provided for the sealing engagement in the inner circumference of the storage neck. The cover 4 is further formed in one piece with a shoulder 52 which is reduced in width compared to the greatest outside width of the device 1 or the head 6 and the cover 50 and which has the snap connection 49 in the starting position the valve 15, and a part of the section 29 and serves on the outer circumference for the radial guidance of the head 6, which overlaps the extension 52 with its inner circumference in any position. In the pump stroke end position, the head 6 expediently strikes the outer end face of the link 50, from which the shoulder 52 protrudes, so that it then lies completely within the head 6.

2, the parts 50a, 51a, 52a, on the other hand, are formed in one piece with the housing 3, on its outer edge ε connect them. The cover 4a lies completely within these parts 50a, 51a, 52a and is fastened via the snap connection 49a, the cover 4a here only engaging with an outer periphery of an annular disk-shaped flange in an inner periphery of the snap member of the housing 3. The head 6 is guided radially with its outer circumference on the inner circumference of the extension 52a and in the pump stroke end position surrounds the snap connection 49a on the outer circumference, it also striking the end wall of the link 50a.

In order to avoid evacuation of the storage due to the media discharge, ventilation is provided, which expediently passes through the discharge device 1 or the base body 2 from the outer end and leads directly along the outer circumference of the pump chamber jacket into the neck of the vessel and from there into the storage space . The ventilation duct 53 runs along the outer circumference of the plunger 13 and the piston body narrowed with respect to the piston lips, the bottom wall of which adjoins the plunger 13 in one piece. These circumferential surfaces and the outer end face of said bottom wall lie opposite inner circumferential and end faces of the cover 4 as channel boundaries with a gap distance. Between the outer circumference of the plunger 13 and the piston bottom wall, a ventilation valve 54 is provided, which in the starting position of the actuation 5 is closed in a pressure-tight manner by a stop and is opened immediately when the actuation begins. The valve 54 is located approximately in the same axial area as the valve 15, the movable valve part being formed in one piece with the tappet 13. The channel 53 lies directly on the inner circumference of that sleeve part of the cover 4 which engages in the inner circumference of the housing 3, opens at the inner end face of this sleeve part, then passes through the casing of the housing 3 between the two sleeve parts of the cover 4 and opens between the casing shell and the seal 51 in the bottle neck. The ventilation duct 53a and the valve 54a according to FIG. 2 are designed in a similar manner, the starting sealing position of the rear sealing lip of the piston 12, which is axially outward in the form of a sleeve, lying directly adjacent to the inner end of the cover sleeve and thereby defining an annular space which ¬ cher against the chamber 14 is closed pressure-tight and forms a section of the ventilation duct.

According to FIGS. 1 and 2, the sections 30, 34, 28, 32, 29 and 33 are provided, starting from the inner end 35 of the component 10, successively and directly integrally adjoining one another, the sections 30, 28, 29 in operation Make length changes and sections 34, 32, 31, 33 do not. Except for section 33, all other sections are ring-shaped in cross-section and closed in the ring wall. In contrast, according to FIG. 3, section 32 is not provided, but only section 31b and the subsequent centering section. Furthermore, section 30b need not be designed to be extendable, but can only allow radial compensating movements. The sleeve-shaped, freely inwardly projecting inner piston lip of the piston 12b here forms the valve seat 19b of the valve 17b. For this purpose, the piston 12b or this lip is extended so far inwards that the sections 28b, 34b are always inside the piston 12b. The outer circumference of section 34b, rounded off as a sliding surface, lies opposite the funnel-shaped, conically enlarged inner circumference 19b of the piston lip in the starting position at a small distance. If the piston 12b is moved inwards, the closing surface 18b of the valve body runs onto the surface 19b and the valve 17b is closed. The pumping chamber 14b here lies only within the piston 12b, and the sections 18b, 34b form an essentially stationary counter-piston, which together with the piston 12b reduces the volume of the pumping chamber 14b during the pumping stroke. The abutment 46b is here extended against the piston 12b in such a way that in the starting position its outer end lies directly adjacent to the inner piston end. The spring or section 30b can be considerably shorter than its width here. This also applies to the annular disk-shaped sections 31 to 34. The section 28 is at most two to three times longer than its width, and the inside or outside width of the sections 28 to 30 is the same.

4, a separate cover 4 is not provided, but the closure 4c is formed solely by the outer piston lip of the piston 12c, which slides on the inner circumference of the shoulder 52c with an annular edge and at the same time forms the valve body of the valve 54c. To form the valve seat or the associated section of the ventilation duct 53, the inner circumference of the neck 52c is provided with longitudinal grooves which are opened immediately after the start of the pump stroke by the valve body in the manner of a slide valve. The outer piston lip has a larger width here than the sliding edge of the inner piston lip, while the two piston lips according to FIGS. 1 to 3 have the same width. The head 6c is secured here with an axial securing means 55 against the continuously one-piece base body 2c, in particular in the starting position almost without play against pulling off. The securing device 55 also serves to limit the starting position of the piston unit 9c, which includes the head 6c. When the parts 2c and 6c or 9c are axially assembled, the securing members snap into each other by themselves, wherein they are formed by a projecting ring collar on the inner circumference of the head shell and a counter collar on the outer end and on the outer circumference of the shoulder 52c.

5, the cover 4d is secured against rotation at the inner end of the component 2d or 3d. The lid 4d det with its outer end face the valve seat 19d, the inlet 24d, the holder 26d, the base 27d and directly with its inner end face the abutment 46d and also the outer boundary of the chamber 22d or the channel 48d. The inner end section of the section 30d has axial transition openings in the jacket 38d, through which the medium can flow from the cavity of the component 10d into the chamber 22d and which extend to the end surface 35d or serve to prevent rotation. The housing 3d forms in one piece at the outer end an annular disk-shaped end wall 56 which is penetrated by the plunger 13d and against the inner end surface of which the piston 12d strikes in the starting position. Furthermore, the housing 3d has on the outer circumference an annular disk protruding and integrally formed with it fastening flange 50d, which is frustoconical in the manner of a plate spring. When this fastening member 50d is clamped against the outer end face of the neck of the vessel with a crimp ring, a screw cap or the like, the flange 50d is pressed back resiliently, its inner end face or its outer peripheral edge forming the seal 51d.

The design of the base body, in particular the arrangement of the cover according to FIG. 5, can also be provided in the embodiments according to FIGS. 1 to 4. The device ld can be installed very easily, particularly in the top position, because the piston unit 9d, the component lOd and finally the cover 4d can be lowered into the housing 3d one after the other and thereby align themselves with inclined surfaces relative to the housing and against one another, with the insertion or snap the cover 4d also snaps the snap connection of the component 10d. The cover 4d engages in the inner circumference of the housing 3d via the snap connection 49d. The housing 3d has from the chamber 14d to for connection 49d the same inside width throughout. The snap connection between the components 10d, 12d can also only be snapped into place after the cover 4d has been snapped in, namely by a stroke of the unit 9d, in which the section 34d strikes the end face 19d and then forms a rigid abutment for the spring 28d.

In FIGS. 1 to 5, the same reference numerals are used for corresponding parts, but with different letter indices, which is why all parts of the description apply mutatis mutandis to all embodiments and all designs of each embodiment can be provided in each of the other embodiments.

In particular in the case of an embodiment according to FIG. 3, it is also possible to guide the outer circumference of the section 28b or 30b very close to the inner circumference of the piston 12b or to have it slide, so that a corresponding spiral channel of the type described results. Furthermore, the transition opening between the cavity of the component 10b and the chamber 22b can be formed by at least one transverse opening in its jacket and / or in the section 31 or 32. If the transition opening lies in section 28b or 30b, its outer circumference can form the valve body of the inlet valve with a section which is axially inwardly offset with respect to the transition opening. The piston can also have a protruding cam or spiral collar on the inner circumference, which engages directly adjacent to section 32 in the spiral groove on the outer circumference of section 28 and thereby forms a connection corresponding to snap connection 43. The inlet valve can furthermore have a valve seat located within the component 10, for example the outer circumference of the tube 25 or the holder 26, onto which an inner circumference of the component 10, for example that of a Section 32 or 31 penetrated through a transverse channel runs as a valve body, the transverse channel and thus the connection between the cavity of component 10 and chamber 14 being closed. In this case, the inlet chamber is formed by this cavity. Instead of the helical design of the respective section 28 to 30, the latter can also be provided with corresponding annular grooves or other profiled axial sections which are each closed over the circumference and lie axially adjacent to one another in the manner of a link.

Claims

Expectations

1. Discharge device for media, such as flowable media, with a basic body (2, 2b, 2c, 2d) provided for receiving the medium, including components, characterized in that at least one of the components has an elongated and a longitudinal axis (11 , 11b, 11c, lld) defining working member (10, 10b, 10c, lOd) and / or that a working member working sections, such as at least two lined up via an intermediate section (31, 32, 34) and at least one spring section (28, 29, 30) has enclosing sections which, in particular, determine essentially full material cross sections or the like transversely and parallel to their longitudinal direction and / or whose cross sections of a respective spring section (28 to 30) can be movable in the longitudinal direction of the spring.

2. Discharge device according to claim 1, characterized gekennzeich¬ net that at least one of the cross sections of at least one intermediate section (31 to 34) in thickness substantially deviates from at least one of the cross sections of at least one spring section (28 to 30) that in particular at least one Spring turn of at least one spring section (28 to 30) parallel to the longitudinal axis (11) has a cross-sectional extension several times greater than radial to the spring section and that preferably at least two adjacent spring turns are formed by an at least two-start spiral and / or a spring turn as a helix has a slope of has more than 10 °.

3. Discharge device according to claim 1 or 2, characterized ge indicates that at least one intermediate section (31 to 34) is arranged or designed to be substantially dimensionally rigid against traction, in particular that an intermediate section (31 to 34) transversely little across the connection end ¬ at least one adjoining spring section (28 to 30) protrudes outwards and that preferably an intermediate section (31, 32, 34) is ring-shaped, and / or that at least one intermediate section (31, 32) counteracts opposite movements parallel to the longitudinal axis ( 11) is secured in position directly against one of the components, in particular that an intermediate section (31, 32) is fastened with a snap connection (43) and that preferably an intermediate section (31, 32) has at least one directly in the component (12 ) engaging position securing member, such as a snap member, a stop collar or the like.

4. Discharge device according to one of the preceding claims, characterized in that at least one intermediate section (33, 34) forms a control element, such as a valve part (18), a stop, a guide member or the like. Of the discharge device that in particular an intermediate section (34) with the connecting ends of the adjoining spring sections (28, 30) can be moved relative to their ends remote from the intermediate section (34) and that preferably an intermediate section (34, 34b) one with a counter surface (19, 19b) of one Component (3, 12b) forms a cooperating closing surface, and / or that at least one end piece (33), which is substantially more rigid than this, is arranged at the end of at least one spring section (29) remote from an intermediate piece (31, 32), that an end piece (33) a control element, such as a valve part (16), a stop, forms a guide member, a control piston or the like. of the discharge device and that preferably one end piece (33) projects transversely outward beyond the connection end of the subsequent spring section (29).

5. discharge device according to one of the preceding Ansprü¬ che, characterized in that approximately in longitudinal section at a distance immediately behind each other and mutually movable sections of at least one Federab¬ section (28 to 30) are directly connected to each other, in particular that at least one spring section (28 to 30) is formed by a jacket body which is essentially closed on the circumference and / or a torsion spring secured against rotation and that preferably at least one spring section (28 to 30) with at least one connecting piece (31 to 34) is essentially continuous Forms hollow body.

6. Discharge device according to one of the preceding claims, characterized in that at least one working section (28 to 34) on the inner and / or outer circumference forms at least one helix (39, 40), such as a helix that in particular a spring section (28 to 30) has a substantially constant wall thickness between its ends and that a spring section (28 to 30) preferably has at least one intermediate piece (31, 32, 34) and / or at least one end piece (33) consist of one piece of plastic or the like.

7. Discharge device according to one of the preceding claims, characterized in that in the longitudinal section at least one intermediate section (31 to 34) has at least one inner surface deviating from the longitudinal direction. that in particular an intermediate section (31 to 34) has at least one inclined inner surface and that preferably an intermediate section (31 to 34) has a helix (39) that extends essentially over the length of its inner surface.

8. discharge device according to one of the preceding claims, characterized in that at least one working member (10) on both sides of at least one intermediate section (31, 32 or 34) separate and jointly and / or independently length-adjustable spring sections ( 28, 29 or 28, 30), that in particular of a working member (10) at least one spring section (28 to 30) as a valve or valve actuation spring and / or a spring section (28, 30) as a return spring is provided for manual actuation (5), and that preferably a working member (10) between two intermediate sections (32, 34) has a main return spring (28) with the greatest spring travel and on the sides of the return spring facing away from this return spring (28) Intermediate sections (32, 34) have valve return springs (29, 30) for an outlet valve (15) and an inlet valve (17), an intermediate section (31, 32), a valve return spring (29) or an end piece (33) can be moved essentially synchronously with a displacement piston (12).

9. Discharge device according to one of the preceding Ansprü¬ che, characterized in that at least one working section (28 to 34) on the inner and / or outer circumference for media guidance or for sliding guidance of the working member (10) is provided, in particular that a Cavity extending over most of the longitudinal extent of at least one working section (28 to 34) is designed as a spring inner space closed at the bottom and that preferably an inlet opening (24) opens within at least one working section (28 to 34) of a working member (10), said inlet opening (24) in the direction of flow, an inlet valve (10) lying on a circumference of the working member (10) 17) is subordinate.

10. Discharge device according to one of the preceding claims, characterized in that at least one basic body (2, 2b, 2c, 2d) consists of only two essentially immovable, separate basic body components (3, 4 or 3d , 4d) and at least one of these components (3, 4) is essentially dimensionally stable, that in particular a base body (2, 2d), a fastening member (50, 50d) for fastening the discharge device (1, ld) to a media store, a seal (51, 51d) for the sealed closure of the media store, a bearing for a displacement piston (12, 12d), at least one valve seat (19, 19d), a ventilation connection (53) for the media store, a holder (26, 26d) for an inlet duct (25,

25d), a feed-through opening for an actuating plunger (13, 13d) and / or a position securing device (55) for an actuating head (6c) and that preferably a base body (2, 2d) at one end with a cover (4th , 4d) which is fastened with a snap connection (49, 49d), forms a support contact surface (46d) for the end of a working member (10d), forms a valve seat (19d) of an inlet valve (17d) , forms an inlet opening (24d) for the medium and / or lies at the end (20d) of the base body (ld) facing away from the actuating end.