EP0309010A1 - Distributeur manuel pour fluide - Google Patents

Distributeur manuel pour fluide Download PDF

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Publication number
EP0309010A1
EP0309010A1 EP88201492A EP88201492A EP0309010A1 EP 0309010 A1 EP0309010 A1 EP 0309010A1 EP 88201492 A EP88201492 A EP 88201492A EP 88201492 A EP88201492 A EP 88201492A EP 0309010 A1 EP0309010 A1 EP 0309010A1
Authority
EP
European Patent Office
Prior art keywords
pump
compressed air
media
nozzle
piston
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP88201492A
Other languages
German (de)
English (en)
Other versions
EP0309010B1 (fr
Inventor
Lothar Graf
Karl-Heinz Fuchs
Leo Märte
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 EP0309010A1 publication Critical patent/EP0309010A1/fr
Application granted granted Critical
Publication of EP0309010B1 publication Critical patent/EP0309010B1/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
    • B05B11/06—Gas or vapour producing the flow, e.g. from a compressible bulb or air pump
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B05—SPRAYING OR ATOMISING IN GENERAL; APPLYING FLUENT MATERIALS TO SURFACES, IN GENERAL
    • B05B—SPRAYING APPARATUS; ATOMISING APPARATUS; NOZZLES
    • B05B7/00—Spraying apparatus for discharge of liquids or other fluent materials from two or more sources, e.g. of liquid and air, of powder and gas
    • B05B7/02—Spray pistols; Apparatus for discharge
    • B05B7/04—Spray pistols; Apparatus for discharge with arrangements for mixing liquids or other fluent materials before discharge
    • B05B7/0416—Spray pistols; Apparatus for discharge with arrangements for mixing liquids or other fluent materials before discharge with arrangements for mixing one gas and one liquid
    • 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
    • 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
    • B05B11/1001—Piston pumps
    • B05B11/1023—Piston pumps having an outlet valve opened by deformation or displacement of the piston relative to its actuating stem
    • 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
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B05—SPRAYING OR ATOMISING IN GENERAL; APPLYING FLUENT MATERIALS TO SURFACES, IN GENERAL
    • B05B—SPRAYING APPARATUS; ATOMISING APPARATUS; NOZZLES
    • B05B7/00—Spraying apparatus for discharge of liquids or other fluent materials from two or more sources, e.g. of liquid and air, of powder and gas
    • B05B7/02—Spray pistols; Apparatus for discharge
    • B05B7/10—Spray pistols; Apparatus for discharge producing a swirling discharge

Definitions

  • the invention relates to a manually operable discharge device for media according to the preamble of claim 1.
  • a further pump is provided, for example, for taking over the pumping work in the overhead position of the discharge device or for pumping a second medium from a separate vessel.
  • the invention has for its object to provide a manually operable discharge device of the type mentioned, which in addition to the pressure source for the media promotion provides a pressure source for providing a pressurized gas stream so that the discharge behavior in the region of the discharge nozzle can be influenced in a simple manner.
  • a discharge device of the type described at the outset according to the invention is characterized by a manually operable pressure source, such as a compressed air pump, to which a compressed air chamber is assigned, which is connected to the discharge nozzle via a compressed air channel.
  • a manually operable pressure source such as a compressed air pump
  • the compressed air pump can be connected directly via a line connection to the discharge nozzle or, for example, to a pressure accumulator formed or separate by the receptacle for the medium, from which the discharge nozzle is then supplied, the pressure in the pressure accumulator simultaneously also for conveying the medium from the vessel into Direction of discharge nozzle can be used.
  • the compressed gas source is used for ultra-fine atomization, for cleaning the line connections for the medium, for valve control and / or for similar purposes, so that even with hand-operated discharge devices of a size that essentially fit into a closed hand or can be easily held and actuated with one hand, can be provided with numerous functions which are otherwise only possible with discharge devices which are connected via lines and pressure sources or pumps and are therefore also connected.
  • the discharge device can thus be a self-contained device that is self-contained as a whole and that is independent of external pressure sources and which is exposed only as a storage vessel for the medium, a cap or the like that closes it and carries the pressure sources. and an actuating unit in the form of, for example, only a single actuating head, so that extremely handy dimensions and a simple structure with high functional reliability result.
  • the discharge device 1 shown in FIGS. 1 to 4 has a thrust piston pump 2 with a cylinder housing 3 to be fastened by a cap 4 on the neck of a vessel 5 provided as a reservoir.
  • the cylinder housing 3 is clamped axially against the end face of the neck of the vessel with an annular flange 6 with the interposition of a seal 42 and is provided axially outside the annular flange 6 in the manner of a cylinder cover with a cylinder cover 7 to be described.
  • This is possible in the area of this outer end Cylinder housing 3 via a radially downwardly projecting transverse wall 8 into a sleeve surrounding it, which has the annular flange 6 at the opposite end.
  • a pre-suction cylinder 15 projecting freely against the piston unit 9 from an annular bottom wall 18 , into which an inlet channel 19 opens, which projects in the opposite direction inwards from the bottom wall 18.
  • the outer circumference of the pre-suction cylinder 15 forms the piston raceway 16 for the pre-suction piston 11 spanning it.
  • the space between the piston raceways 13, 16 forms the pump chamber 14, in which the pre-suction chamber 17 delimited by the pre-suction cylinder 15 and by the pre-suction piston 11 is located, in which a return spring 20 loading the piston unit 9 to the initial position is arranged.
  • the outer or rear end of the pump piston 10 is provided with a tubular piston shaft lying on its axis and guided outwards through the cylinder cover 7, which limits an outlet channel 24 connected to the pump chamber 14 with the interposition of an outlet valve 23.
  • the outlet channel 24 leads to a discharge nozzle 25 in a handle 22 arranged at the outer end of the piston skirt 21 in the form of an actuating head which engages over the sleeve of the cylinder housing 3 with a small gap distance in every position.
  • An end wall of the suction piston 11 opposite the suction chamber 14 forms a frusto-conical valve closing part 26 of the outlet valve 23, the valve seat 27 of which is provided on an associated end wall of the pump piston 10.
  • a shaft 28 slidably projects into the piston shaft 21 to open the outlet valve 23.
  • a section of the piston shaft 21 adjoining the pump piston 10 forms an elastically resiliently compressible neck 29.
  • the outlet valve 23 When the discharge device is actuated by depressing the handle 22, the outlet valve 23 is opened by differential pressure when a predetermined pressure is reached.
  • a transfer valve 32 is provided which, depending on the path, is only opened via a last section of the return stroke movement of the piston unit which reaches the starting position and is closed during the largest part of the pump stroke which reaches the pump stroke end position.
  • the valve closing part 33 of this slide valve is formed by the front piston lip of the pre-suction piston 11, to which approximately axial valve slots 39 are assigned as valve openings at the free end of the pre-suction cylinder 15.
  • the transfer valve 32 is closed and, accordingly, it is suddenly opened again when the priming piston 11 returns after a vacuum has been built up in the pump chamber 14.
  • the two end faces 30, 31 of the pump piston 10 and the pre-suction piston 11 can strike the bottom wall 18 with a time delay in such a way that the outlet valve 23 is opened, if necessary, for venting the pump chamber 14.
  • the cup-shaped suction piston 11 has a piston sleeve 35 which forms the end face 30 and extends approximately over the entire length of a piston sleeve 36 of the pump piston 10.
  • the piston shaft 21 has a driver 40 opposite the end of the shaft 28 at a short distance, which runs against the shaft 28 when the neck 29 is shortened after the pump piston 10 strikes in the pump stroke end position and thereby opens the outlet valve 23.
  • the push piston pump 2 also has a path-dependent, valve-controlled ventilation for the vessel 5. Between the two piston lips of the pump piston 10 3 ventilation through openings 43 are provided in the jacket of the cylinder housing, which are located immediately adjacent to the outside of the seal 42 in the region of an annular gap which is delimited by the seal 42 and the outer circumference of the cylinder housing 3. The through openings are provided at the end of longitudinal channels 44, which are released to the outside at least towards the end of the pump stroke by the rear piston lip of the pump piston 10 in order to produce the ventilation connection.
  • the discharge device 1 can, in particular with regard to the parts or assemblies described, be designed in accordance with DE patent application P 37 15 301.3, to which reference is made for further details and effects.
  • the pump can also be operated by a completely different, manually operated pump type, for example a bellows pump, a diaphragm pump, a balloon pump or the like. be educated. It is also conceivable to design the media pump so that it initially creates a prestressed pressure in the vessel 5 and thereby the medium is conveyed via a riser pipe to the outlet channel and to the discharge nozzle 25, as is the case, for example, in DE patent application P 37 12 327.0 is described.
  • the discharge device 1 is assigned a preferably manually operated compressed air pump 50 as a compressed air source, which is structurally separate from the media pump 2 or the vessel 5 and, if appropriate, can also be designed as a foot-operated pump and which is then expediently provided via a line, such as a flexible one Hose connected to the vessel or the part of the discharge device 1 arranged thereon is.
  • This compressed air pump can also be formed by different pump types, for example the pump types explained using the media pump.
  • the compressed air pump 50 is designed as a thrust piston pump, structurally combined with the discharge device 1, to be operated essentially simultaneously with the same handle 22 as the media pump 2 and coaxially within and / or axially immediately adjacent to the media pump 2, and expediently afterwards arranged at the outer end.
  • the compressed air pump 50 with the interposition of a pressure accumulator to be charged with it via a manually operable valve to the discharge channel 24 or to the discharge nozzle 25, the result is a particularly simple design if the compressed air pump 50 is connected directly, so that compressed air in the is funded only during the activity.
  • the compressed air pump 50 has a pump piston 51, a pump cylinder 52 receiving it, an air inlet valve 53 integrated with the pump piston 53, and an air outlet valve 54 structurally combined with the pump cylinder 52, which are essentially axially aligned with one another and in the central axis of the media pump 2 are arranged completely within the outer limits of the cap-shaped handle 22.
  • a preferred embodiment results if the pump piston 51 is arranged fixedly relative to this housing or to the cylinder housing 3 and the pump cylinder 52 is movable with the handle 22.
  • the pump cylinder 52 is directly through which the without requiring a separate cylinder housing for the compressed air pump 50
  • Sleeve 46 of the cylinder housing 3 overlapping cap jacket of the handle 22 is formed, the inner circumference of which over part of its length forms the piston race 55 for a radially outer piston lip 56 of the pump piston 51 which is widened at an acute angle to the cap end wall of the handle 2.
  • a corresponding, radially inner, but conically tapered piston lip 57 of the pump piston 51 runs on the cylindrical outer circumference of a section of the piston shaft 21 which adjoins the neck 29 and extends almost up to the connection with the handle 2.
  • the pumping piston 51 has on its end facing away from the piston lips 56, 57 an approximately annular snap member 58 for attachment, which is blown into an annular groove in the form of an inner groove on a collar-shaped extension 59, which extends the sleeve 86 from the side facing away from it the transverse wall 8 protrudes slightly, so that the pump piston 51 is axially supported against the pump pressure by abutment on the transverse wall 8.
  • the cylinder cover 7 is also provided in the form of ribs which protrude radially into the region of the associated enlarged section of the cylinder bore of the cylinder housing 3 and are distributed uniformly around the pump axis and which are made in one piece with the cylinder housing 3 or with the relatively soft material existing pump piston 51 can be formed so that in the starting position the pump piston 10 of the media pump 2 can strike the cylinder cover 7 with its rear piston lip relatively softly.
  • the cap jacket or the pump cylinder 52 or the like may have a sealing lip. sealed to run against the sleeve 46 so that the housing or the associated part of the cylinder housing 3 can form the pump piston directly in one piece.
  • the gap between the pump cylinder 52 and the housing expediently forms one Entry slot of the ventilation air for the vessel 5 and / or for the intake air for the compressed air pump 50, which expediently past the outer circumference of the pump piston 51 between interruptions or breakthroughs in the snap member 58, the intake air through the pump piston 51 away from the piston lips 56, 57 Sucks back.
  • air passage openings are provided in a ring-shaped bottom wall connecting the piston lips 56, 57 in a ring and can be closed with an annular disk-shaped valve body 60 made of elastic material in the manner of a non-prestressed check valve.
  • the valve body 60 lies on the inside of the bottom wall between the piston lips 56, 57 and is stop-limited in the opening direction by at least one, in particular two, coaxial annular beads 61, which are provided on the facing circumferential sides of the piston lips 56, 57 at a distance from the bottom wall, which is only slightly larger than the thickness of the valve body 60.
  • the smaller in diameter, but similarly designed outlet valve 54 works in the manner of a prestressed pressure relief valve which only opens when a predetermined pressure is reached in the pump or pressure chamber 62 and opens the path for the compressed air to the discharge nozzle 25.
  • a collar-shaped insert 64 is inserted with its flange-like collar and secured by a snap connection so that the collar is approximately flush with the free end face the sleeve 63 closes.
  • passage openings are arranged in a ring, which can be closed with a ring-shaped valve body 65.
  • valve body 65 is due to the end face of the collar of the insert 63 facing away from the pressure chamber 62 under the force of a valve spring 66 designed as a helical compression spring, which is arranged in an annular gap between the sleeve 63 and a further plug-in sleeve 67 of the handle 22 lying coaxially within it.
  • a valve spring 66 designed as a helical compression spring, which is arranged in an annular gap between the sleeve 63 and a further plug-in sleeve 67 of the handle 22 lying coaxially within it.
  • the sleeve portion of the insert 64 is inserted, in which in turn the associated end of the piston shaft 21 with reduced outer diameter is inserted in the manner of a press fit such that an essentially rigid connection is formed between the piston shaft 21 and the handle 22 , wherein the free end faces of the piston shaft 21 and the sleeve portion of the insert 64 are flush with each other close to the cap end face of the handle 22 and the driver 40 is provided in the associated end region of the piston shaft 21.
  • the discharge nozzle 25 is essentially formed by four bodies lying approximately coaxially and transversely or at right angles to the central axis of the media pump 2 or the compressed air pump 50, namely intermeshed nozzle caps 70, 71, an inner body 71 engaging in the inner nozzle cap 71 and an outer nozzle cap 70 on the outer circumference receiving outer sleeve 73, which is made in one piece with the inner body 72 or how this can be formed with the handle and expediently connects both to the jacket of the sleeve 63 and to the cap end wall of the handle 22.
  • the end walls of the nozzle caps 70, 71 which are essentially perpendicular to the nozzle axis 69, form nozzle end plates 74, 75, which abut one another almost over the entire surface, the end face 76 of the inner body 72 abutting approximately the entire surface on the inner end face of the rear body 75, and the front nozzle end plate 74 opposite the one front end face 77 of the outer sleeve 73 is set back by less than half of its inner diameter corresponding to the outer diameter of the outer nozzle cap 70.
  • the Nozzle end plate 75 is thickened towards the nozzle axis by the spherically projecting configuration of its outer end face 78 and, with this end face 78, lies essentially over the entire surface of a correspondingly concave section of the inner end face of the nozzle end plate 74.
  • the nozzle end opening 80 leading to the outside lies approximately in the outer end face of the nozzle end plate 74 or is slightly set back in relation to this in the bottom surface of a flat, cow-shaped recess 79, so that the nozzle end opening 80 in the manner described is opposite the front end of the outer sleeve 73 and from it shielded from the front.
  • the nozzle channel of the discharge nozzle 25 is essentially formed by two separate individual channels or individual nozzles 81, 82, which are immediately behind one another in the same axis.
  • the front individual nozzle 81 formed by a corresponding nozzle channel in the nozzle end plate 74, the nozzle outlet opening of which is formed by the nozzle end opening 80, has a length which is smaller than its mean or smallest width and is of one length in the region of the inner one over its entire length End face of the nozzle end plate 74 lying nozzle inlet opening 83 to the nozzle outlet opening continuously widened conically at an acute angle.
  • the rear individual nozzle 82 formed by a nozzle channel in the nozzle end plate 75 has a greater length compared to its mean diameter, but is smaller compared to its largest diameter, and is narrowed in the direction of the fault or in the direction of the individual nozzle 81 in front of it, with a longer rear section of an associated associated nozzle inlet opening 85, which is located approximately in the inner end face of the nozzle end plate 75, is tapered at an acute angle, and a section of constant width is tied to its smallest diameter or constant diameter, which extends to the associated nozzle outlet opening 84 located in the end face 78, so that there is both a continuous and a gradual narrowing of this individual nozzle 82 to a smallest width, which is slightly smaller than the smallest width of the Single nozzle 81 is.
  • a swirl device 86 which is formed in one piece with at least one of the two nozzle end plates, in particular with the front nozzle end plate 74, and which is formed by a swirl chamber which is further than the inlet opening 83 and the outlet opening 84, but whose axial extent is considerably smaller than which is at least one, in particular the shorter, individual nozzle 81.
  • the nozzle inlet opening 85 of the rear individual nozzle 82 is also assigned a swirl device 87, which is likewise formed by a swirl chamber which is essentially in the nozzle axis and which is further compared to the inlet opening 85, but substantially flatter compared to the length of the individual nozzle mentioned, and which is integral with the Inner body 72 and / or the nozzle end plate 75 can be formed.
  • the swirl devices 86, 87 and the associated feed lines can be formed in one piece with a single nozzle body in that only this one on the inner and outer end face of the associated nozzle face plate 75 with the corresponding shapes that deviate from the smooth shape, namely with corresponding shapes Depressions is provided.
  • the discharge nozzle 25 can be adapted to the properties of the respective fluid to be atomized by changing only a single component. It is also conceivable to provide three or more individual nozzles, for example for guiding compressed air into the media stream in succession or for feeding the medium or two or more different media in separate streams to the discharge nozzle 25.
  • the rear individual nozzle 82 or its swirl device 87 is connected to the media outlet channel 24 via a channel section 88 provided as an end section, while the front individual nozzle 81 or its swirl device 86 via a channel section 89 provided as an end section adjoins an outlet valve 54 Compressed air duct 90 is connected.
  • the media channel section 88 which is angular in cross section, is formed by corresponding grooves on the inner circumferential surface and on the inner end face of the inner nozzle cap 71 and is delimited by this and the inner body 72, and furthermore via an intermediate channel with the outer end of the piston skirt 21 or the outlet channel 24 connected, the intermediate channel being sealed against the guidance of the compressed air between the inner body 72 and the cap end wall of the handle 22.
  • the compressed air channel section 89 is correspondingly angular and expediently offset diametrically around the nozzle axis relative to the channel section 88 between the cap sleeves and the nozzle end plates 74, 75 of the nozzle caps 70, 71 and is formed by corresponding axial and radial grooves which are formed on the outer surface of the nozzle cap 71 can be provided, but are provided in the illustrated embodiment on the inside of the nozzle cap 70.
  • the annular gap accommodating the valve spring 66 is included in the compressed air channel 90, up to which the compressed air channel section 89 extends approximately with its axial section.
  • the radial end sections of the channel sections 88, 89 are connected essentially radially or tangentially to the respectively associated swirl chamber, so that the medium conveyed in the area of the associated nozzle inlet opening 85, 83 flows rotatingly or swirled around the nozzle axis and thus into the each associated nozzle duct enters.
  • the configuration described forms an at least two-stage or multi-stage atomizer device 100, with which the media flow in the region of the swirl device 87 and the individual nozzle 82 is pre-atomized into material particles with a particle size of, for example, about 50-70 ⁇ m, and then at least one further by compressed air acceleration
  • the atomization is finer, whereby the air after-atomization can achieve a particle size of the material particles that is up to approximately a power of ten. This is particularly the case if the dimensions for achieving a Laval effect are such that the compressed air flow accelerates the material particles approximately to or even above the speed of sound and then, upon impacting the atmosphere, immediately tearing them apart as soon as they exit the nozzle opening 80 under the impact force will.
  • the nozzle geometry of the front individual nozzles 81 it is expedient if it has a relatively small width in the region of its nozzle inlet opening and becomes very far from it directly via a soft, trumpet-shaped transition or conical surfaces.
  • the smallest width of the individual nozzle 81 is expediently less than 2 or 1.5 mm, preferably less than 1 mm and more than a tenth of a millimeter, an order of magnitude of half a millimeter being preferred.
  • the individual nozzle 82 which is designed as a hollow cone nozzle, has a smaller, smallest width, which is expedient approximately in the order of half the smallest width of the individual nozzle 81 or even less, and can be up to less than a tenth of a millimeter, preferably between one and two tenths of a millimeter is.
  • the speed of sound in the outlet of the individual nozzle 81 is approximately reached and it is theoretically a droplet size of the atomized rivers liquid up to 0.632 ⁇ m achievable, but practically because of the compressibility of the air to reach a value of up to 5 ⁇ m.
  • this chamber or of the swirl chamber is expediently of the order of magnitude of the smallest width of the individual nozzle 82 or of the order of a fraction of the smallest width of the individual nozzle 81, which is, for example, about a fifth, and expediently below one millimeter or half a millimeter and preferably on the order of a tenth of a millimeter.
  • a baffle member can also be provided in front of the nozzle end opening 80 and opposite it, against which the liquid is thrown and thereby atomized and deflected transversely to the nozzle axis, with the supply of sound only then, for example, by using the Laval effect - or supersonic speed of accelerated compressed air flow can take place.
  • the nozzle outlet opening for the compressed air can be provided, for example, in a ring around the nozzle outlet opening for the liquid or around the plate-shaped impact member, so that the compressed air takes over the pre-atomized liquid at the edge of the impact member and redirects it again parallel to the nozzle axis direction, so that the liquid particles so accelerated by the compressed air are thrown against the atmosphere and are broken down even more finely by bursting under the pressure that occurs.
  • the compressed air is mixed in before the individual nozzle 81, so that a media / compressed air mixture already exits through the end or individual nozzle 81.
  • the media nozzle can also be designed as another nozzle, for example as a full cone nozzle, as a rectangular cone nozzle, as a flat jet nozzle or as an axial swirl nozzle or as a two- or multi-component nozzle, depending on the requirements to be met of the medium to be processed. Training as a double hollow cone nozzle is also conceivable. Above all, it can be advantageous if the discharge nozzle is designed as an ultrasonic nozzle with longitudinal and / or circular capillary waves.
  • both the media pump 2 and the compressed air pump 50 start the pump stroke against the single common return spring 20.
  • the same return spring 20 also keeps the outlet valve 23 closed as a valve spring. After a first stroke distance corresponding to a fraction of, for example, about a quarter of the total stroke, the suction or transfer valve 32 is closed and a fluid overpressure is generated in the pump chamber 14, provided that the medium to be discharged is filled.
  • the two pump streams of medium and compressed gas are supplied separately to the discharge nozzle 25 via separate conduit paths and are only combined in the area of the mixing chamber or swirl chamber 86 after the medium has already been atomized within the intermediate space.
  • the discharge device is suitable both for medicinal substances, for example inhalation preparations, and for technical applications for spraying paints, for example water-soluble paints, oils, for chemical substances and much more, without the need to store propellant gas in the vessel 5 for atomization.
  • An example of a cartridge-shaped compressed gas reservoir with an outlet valve can also be provided as the compressed gas source, which can then be opened expediently by actuating the handle 22.
  • the handle 22 is relieved by release, as a result of which the media outlet valve 23 closes under the force of the return spring 20.
  • the compressed gas outlet valve 54 can be adjusted so that it closes before, simultaneously with or after the media outlet valve 23, so that in the latter case this discharge nozzle 25 by the still flowing compressed air Media residues are cleaned or blown free.
  • the return spring 20 takes the entire piston unit 9 and the compressed air pump cylinder 52 to the starting position, so that a negative pressure builds up in the pump chamber 14 and through a riser tube 47 arranged on the inlet channel 19 and reaching almost to the bottom of the vessel the pre-suction chamber 17 is sucked in.
  • the compressed air inlet valve 53 is opened under the vacuum created in the pressure chamber 62, so that when the outlet valve 54 is closed, air into the between the rear end of the piston unit 9 or the pump piston 10 and the rear of the compressed air pump piston 51 and through it Pressure chamber 62 is sucked.
  • the transfer valve 32 is opened by releasing the valve slots 39, the liquid passes from the pre-suction chamber 17 into the pump chamber 14, so that it is filled again and the discharge device is ready for a next pumping stroke.
  • the ventilation connection to the vessel 5 is also tightly closed by the rear piston lip of the pump piston 10, while during the pumping stroke it is open at the latest after opening the transfer valve 32.
  • the design described enables a very precise metering of the amount of media discharged per pump stroke to be achieved, and the discharge device can be designed with a simple and compact design in such a way that it works equally well practically regardless of position or in both an upright and upside down position and even in an upside down position when the piston unit is in the initial position, the discharge device prevents the vessel from leaking.
  • the nozzle channel of the end individual nozzle 81a is also stepped in cross section, with a distance of constant width adjoining the inlet opening 83a, which merges into an obtuse-angled conical section of approximately the same length, the wide end of which is the nozzle end opening 80a forms.
  • the nozzle outlet opening 84a of the individual media nozzle 82 is formed by an annular edge which is sharp in cross-section and has an inner flank parallel to the nozzle axis 69a.
  • the compressed air flow or the channel section 89a opens out in the region of this flow tear-off edge 91, which lies in the plane of the end face of the mixing chamber 86a opposite the individual nozzle 81a and is surrounded by an obtuse V-shaped annular groove in cross section such that one side flank of the ring outer Flank of the tear-off edge 91 forms.
  • This annular groove 92 can form part of the swirl device for the compressed air, which thus rotates around the tear-off edge 91 or on its outer flank.
  • the tear-off edge can be formed by an end edge or a radially inwardly directed peripheral edge and also by the entry region of the front individual nozzle.
  • the axial extent of the individual nozzle 81a is substantially smaller than that of the individual nozzle 82a, while the diameter of the inlet opening 83a corresponds approximately to the diameter of the deepest point of the annular groove 92.
  • the mouth of the compressed gas channel surrounds the nozzle axis 69b with the chamber 86b such that the two pressure flows only meet in the area of the nozzle channel of the individual nozzle 81b and / or in the discharge direction thereafter, the compressed air flow being directed, if necessary, as parallel to the axis of the nozzle axis 69b. rotating enveloping stream around the pre-atomized Media stream is supplied.
  • the nozzle outlet opening 84b is surrounded by an annular end face 91b of the individual nozzle 82b which is perpendicular to the nozzle axis 69b, this end face merging on the outer circumference into the inner ring flank of the chamber 86b, which is formed by an annular groove 92b formed in the associated end face 78b is.
  • the outer width of the end face 91b is smaller than the inner width of the inlet opening 83b, which thus surrounds the outlet opening 84b in a ring.
  • the end face 91b which could also be frusto-conical in shape, lies at least approximately in the plane of the inlet opening 83b, with a position of the outlet opening 84b also between the two ends of the nozzle channel of the individual nozzle 81b or with respect to its outer end or with respect to the nozzle end opening 80b is conceivable offset to the outside.
  • the discharge nozzle 25b expediently has at least two individual nozzles 81b, 82b, which are directly adjacent to one another, in particular in the direction of their nozzle axis 69b and / or are approximately concentric, one of which preferably forms the nozzle end opening 80b as the end individual nozzle 81b and the other only the individual media nozzle 82b connected to the media outlet channel can be set back relative to the nozzle end opening 80b.
  • the annular nozzle channel delimited by these two nozzles is expediently conically narrowed outwards or in the discharge direction, for example, by narrowing both the outer circumference of the inner nozzle and the inner circumference of the outer nozzle , wherein the cone angle of these two circumferential surfaces can be provided so that they deviate from each other in such a way that the annular nozzle channel provided for the compressed air flow decreases slightly towards the outside in the passage cross section.
  • the nozzle channel of the individual media nozzle can widen a front, funnel-shaped, the associated outlet have opening-forming end portion, so that, for example, this nozzle channel has a constriction between its ends, from which it is flared and / or stepped towards both ends.
  • FIG. 7 to 9 show two swirl devices 86c, 87c on a discharge nozzle 25c, which is designed similarly to that according to FIG. 6.
  • the channel section 89c or 88c opens into the associated swirl device 86c or 87c in the region of an annular channel surrounding the nozzle axis 69c, the opening being able to be provided radially or tangentially in accordance with the associated swirl direction, so that the compressed air is already in the annular channel 93, 94 flows circumferentially in the swirl direction.
  • guide channels 95 or 96 branch inwards, which are delimited by guide bodies formed in one piece with the respectively associated nozzle body, have a substantially smaller passage cross section than the ring channel 93 or 94 and in which associated flow direction can be continuously narrowed or of constant cross-section.
  • one guide channel or two, three, four or more guide channels can be provided evenly distributed around the central axis, the sum of the passage cross sections of the guide channels 95 and 96 expediently being greater than that of the associated ring channel 93 and 94, respectively.
  • the guide channels 95 and 96 open into an interior space delimited by the associated guide bodies which, in the case of the swirl device 87c, the rear end of the nozzle channel of the individual nozzle 82c and in the case of the swirl device 86c the annular ring surrounding the individual nozzle 82c or the entry region of the individual nozzle 81c Space is.
  • the guide channels 95, 96 can open tangentially into this respective associated interior space in such a way that the direction of rotation of the two pressure streams is the same or opposite, with a particularly high loading in the first case acceleration and in the second case a particularly strong swirl is achieved.
  • the swirl devices 86c, 87c or the guide bodies and the lateral boundaries of the guide channels 95, 96 are formed exclusively by appropriate shaping of the end faces of the nozzle end plate 75c or the nozzle cap 71 which face away from one another, so that the end faces of the inner body 72c and of the nozzle end plate 74c can be made flat and only serve to delimit the channels and chambers on one side.
  • FIG. 10 shows a double-rotation discharge nozzle 25d, in which the medium in the swirling or swirling device 87d is brought into a corresponding flow in a first stage and then in a second swirling or swirling device 86d again in an identical manner. or, if necessary, oppositely directed swirl flow, in particular under acceleration.
  • the outlet opening 84d of the nozzle channel of the individual nozzle 82d opens outside the nozzle axis 69d and / or is oriented obliquely with respect thereto, for which purpose in the exemplary embodiment shown there is a nozzle channel lying at an angle of approximately 45 ° or more to the nozzle axis 69d, the inlet opening 85d of which is eccentric or is at a distance from the nozzle axis 69d.
  • the compressed air can be supplied in the swirl chamber 86d or in a further, subsequent separate chamber.
  • FIG. 11 shows a discharge device 1e, in which the handle 22e actuates only the compressed air pump 50e and only then also the media pump 2e at the beginning of its actuation path associated with the pump stroke, whereby before preferably an actuating rod provided for both pumps and, in the exemplary embodiment shown, formed by the piston rod 21e has a stop-limited free travel until the entrainment or actuation of the media pump 2e.
  • the arrangement can instead or in addition also be provided in such a way that the handle 22e at the end of the pump stroke of the media pump 2e has a follow-up or remaining path for the subsequent further actuation of the compressed air pump 50e, so that the compressed air pump 50e also after the end of the pump stroke the media pump 2e can be operated in a continuous continuation of its already performed pumping stroke over a residual stroke.
  • an overpressure is built up at least in the pressure chamber 62e or even, if the outlet valve 54e, which is designed as a spring-loaded plate valve, is appropriately matched, due to the free travel before the pump stroke of the media pump 2e or before or after the closing of its inlet or transfer valve, Compressed air is fed into the discharge nozzle 25e before opening the media outlet valve 23e.
  • compressed air continues to be fed to the discharge nozzle 25e, and this can be used to clean it or to blow it free of any residual particles of the medium.
  • the piston rod 21e is designed as a tubular telescopic rod that is spring-loaded to the extended position, one outer rod part 97 of which forms a component with the pumping piston 10e and the other inner rod part 98 is firmly connected to the insert 64e via the insert 64e Handle 22e is connected.
  • an extension spring 99 in the form of a helical compression spring having one end, the other end of which is supported on the end face of the inner rod part 98 ge is supported relative to the rod part 97 and, as shown, can also be supported on the pre-suction piston 11e or on the valve closing part 26e of the media outlet valve 23e, so that the tension spring 99 counteracts its valve spring and, when a predetermined spring tension is reached, the opening, which is essentially path-dependent, is then reached Exhaust valve 23e can initiate.
  • the stretching spring 99 can have a graduated spring characteristic in itself or in cooperation with a further spring which is effective only after a predetermined relative displacement of the rod parts 97, 98 in such a way that the resistance exerted by the stretching spring 99 in a first stage against the force of the return spring of the media pump 2e is so low that at the beginning of the actuation path of the handle 22e only the compressed air pump 50e is actuated and the media pump 2e remains unactuated. In a second stage, the resistance of the extension spring 99 abruptly increases so much with respect to the return spring of the media pump 2e that it is actuated in essentially the same manner with the compressed air pump 50e.
  • the pump stroke end position of the compressed air pump 50e is expediently limited by the stop of the handle 22e with respect to the piston unit 9e or with respect to the end face of the rod part 97 of the piston rod 21e, against which the end face of the sleeve 63e or the insert 64e strikes.
  • the outlet channel 24e is provided on the outer circumference of the shaft 28, in the embodiment according to FIG. 11 it is provided inside the tubular shaft 28e.
  • the pump chamber 14, if it is not yet filled with medium, can thereby be relatively ßig easily vented that at the end of the pump stroke of the media pump 2, the pump piston 10 is fixed by a stop and then by further pressing the handle 22 via the driver 40, the outlet valve 23 can be opened mechanically or depending on the path.
  • Such an arrangement is not provided in the embodiment according to FIG. 11, but would also be conceivable if the driver only reached the end of the shaft 28e shortly before the pump stroke end position of the compressed air pump 50e.
  • the shaft 28e is slidably guided in the rod part 98 and surrounded by the extension spring 99 lying inside the rod part 97.
  • the compressed air pump 50e or the handle 22e in the starting position is stop-limited by a stop directly against a housing part, in particular with respect to the sleeve 46e or the shoulder 59e of the cylinder housing 3e of the media pump 2e.
  • the pump piston 52e has at its end an inwardly directed annular collar as a stop 101, to which a ring collar of the cylinder housing 3e which projects beyond the outer circumference and lies in the region of the counter-member for the snap member 58e is assigned as a counter-stop 102.
  • the stop 101 and the counter-stop 102 can rest against one another in a sealed manner in the starting position such that the air supply to the compressed air pump 50e and the ventilation for the vessel are hermetically sealed to the outside.
  • the media outlet valve 23e is provided lying in the region of the pump piston 10e or in the associated cylinder housing 3e, and the media outlet channel 24e in the flow direction after this, outlet valve opening into the annular space between the shaft 28e and the rod part 97e 23e is connected to the annular space via transverse bores in the shaft 28e, in the embodiment according to FIG. 12 the media outlet valve 23f is outside the cylinder housing 3f in the region of the compressed air pump 50f or provided within the push-in sleeve 67f of the handle 22f, in which case the handle or the compressed air pump cylinder 52f forms part of the piston shaft 21f.
  • the outlet valve 23f can, as shown, be designed in the manner of a needle or pin valve, in the manner of a check valve, in the manner of a control piston-operated valve influenced by the media pressure and in particular also as a hose valve according to DE-PS 29 02 624.
  • the discharge valve 53f is very close to the discharge nozzle 25f or directly on the side of the inner body 72f facing away from it, so that between it and the nozzle channel there is practically only the angular channel section 88f, in which only small media residues can remain and which can be caused by corresponding Reversing the compressed air can also be easily cleaned or blown free.
  • the compressed air outlet valve 54f is a spring-loaded ball valve in the illustrated embodiment, the valve housing formed by the cylinder housing of the compressed air pump or the handle 22f between the pump axis and the discharge nozzle 25f so that it is directly connected to one leg of the compressed air duct section 89f .
  • the compressed air pump cylinder 52f engages with a small gap distance in the inner circumference of the collar-shaped extension 59f, which, like the transverse wall 8f, is formed in one piece with the cap 4f designed as a screw cap.
  • the media pump 2f does not have a double piston, but only a single pump piston 10f on the piston unit 9f, which is essentially formed by an annular piston disk, over the front and / or rear end of which protrudes a frustoconically enlarged piston lip, the front one Piston lip in the pump stroke end position on the by a stepped ring shoulder
  • the formed bottom wall 18f strikes, which merges in the direction of the inlet duct 19 into a multiply offset end portion of the cylinder housing 3f which is reduced in the outer circumference.
  • this end section there is a non-return valve in the form of a ball valve with a spherical valve closing part 33f and a conical valve seat 34f as a suction valve 32f.
  • the cylinder housing 3f is formed in one piece with the annular flange 6f projecting at its outer end over the outer circumference, which is supported on the transverse wall 8f with its free end face and can be tensioned against the neck of the vessel with the annular end face remote therefrom so that it itself the seal 42 corresponding seal forms.
  • the cylinder 12 or the cylinder housing 3f is closed with an annular or sleeve-shaped cylinder cover 7f through which the piston skirt 21f passes, which is sealed with an annular collar projecting beyond its outer circumference so that it is also pressed into an inner groove of the annular flange 6f can be axially supported on the transverse wall 8f.
  • An inner end of the cylinder cover 7f which projects into the jacket of the cylinder housing 3f and has the shape of a truncated cone on the outer periphery corresponding to the rear piston lip of the pump piston 10f, lies in the starting position of the pump piston 10f as a stop with a relatively sharp ring edge on the pump piston 10f or on the rear end face of the piston disc, whereby a seal against the compressed air pump 50f is achieved.
  • the piston shaft 21f can be displaced from the starting position with respect to the pump piston 10f by an empty travel, via which the compressed air pump 50f is already actuated, while the media pump 2f is still not actuated due to the pump piston 10f remaining stationary. At the end of the free travel, the piston shaft 21f hits the piston with a driver on the back Washer of the pump piston 10f and then takes it to its end of stroke position.
  • the driver 103 lying outside the compressed air pump 50f in the starting position within the cylinder cover 7f is formed by an annular shoulder of the piston shaft 21f, which in turn is formed by the end face of the rod part 98f which is connected or formed in one piece to the pump cylinder 52f or the handle 22f, which is one in the External cross section can form a reduced continuation of the sleeve 67f.
  • the piston shaft 21f is designed in the manner of a telescopic rod, the inner tubular part 28f of which forms the outlet channel 24f and forms the valve closing part 26f in the region of the associated end.
  • the piston shaft 22f or the rod part 28f passes through the pump piston 10f in the region of a passage opening in the piston disc, the pump piston 10f having at least one sealing lip on the inner circumference for sealed guidance on the outer circumference of this rod part 28f.
  • the rod part 28f has a rod collar 105 projecting beyond its outer circumference or a comparable driving member for the return stroke of the pump piston 10f, which abuts the associated end face of the piston disc and on which the return spring 40f can be supported.
  • the outer and inner piston lips 56f and 57f of the pump piston 51f of the compressed air pump 50f are axially offset from one another by more than the pump stroke of the media pump 2f or the compressed air pump 50f, the inner piston lip 57f expediently essentially within the ring flange 6f or of the cylinder housing 3f, while the outer piston lip 56f, on the other hand, is offset outwards and can extend at least to the outer end of the projection 59f or beyond.
  • the Pumpkol ben 51f is centered in the cylinder cover 7f or the ring flange 6f and also in the transverse wall 8f and sealed except for the air supply, for which purpose it has a profiled jacket part which is stepped several times on the outer circumference between its bottom wall and the piston lip.
  • FIG. 13 shows an advantageous embodiment of a control device 106 for opening the media outlet channel 24h or the compressed air channel 90h or both channels with a delay compared to the way of the handle 22h, preferably a control piston 107 influenced by the pressure of the compressed air in the compressed air chamber 62h Actuation of at least one movable valve body 27h or 65h is provided.
  • the control piston 107 which is spring-loaded in the closing direction, is structurally combined with the valve body 65h of the compressed air outlet valve 54h, with which it forms a cup-shaped collar sleeve, the annular collar provided at one end of which forms the valve body 65h and which is closed at the other end with an annular disk-shaped bottom wall, which forms the valve seat 27h with an extension projecting into the piston shaft 21h against the direction of flow, to which a valve seat part 26h can be assigned a part which is fixed in the piston shaft 21h or which is movable with the shaft 28h.
  • the control piston 107 is guided with its jacket on the outer circumference of the associated end of the piston shaft 21h or the surrounding sleeve part of the insert 64h so as to be displaceable by the opening path of the two valves against the common valve spring 66h.
  • the control piston 107 is guided with a sealing lip 108 located in the region of its bottom wall on a raceway of the sleeve 63, this raceway then being connected to the annular gap is provided for the valve spring 66h.
  • the control device 106 for the joint control of both the compressed gas and the medium with regard to their release to the discharge nozzle 25h opens both valves simultaneously or successively when the predetermined pressure in the pressure chamber 62h is reached in that the valve closing part 65h of the exhaust valve 54h is first brought into the open position by this overpressure becomes.
  • the control piston 107 is carried along by the valve closing part 65h, so that the valve seat 27h provided on it lifts off from the valve closing part 26h simultaneously or with a delay and thereby also opens.
  • the media outlet valve 23h can close again simultaneously with or before the compressed air outlet valve 54h.
  • the control device 107 thus has at least one valve leading to the individual media nozzle and at least one valve leading to the individual compressed air nozzle, the valve leading to the individual compressed air nozzle preferably opening before and / or closing after the other valve.
  • control device 106i for reversing at least a portion of the compressed air flow coming from the pressure chamber into at least a partial section, in particular an end section adjoining the discharge nozzle 25i or into the discharge nozzle 25i, preferably a control piston 107i influenced by the pressure of the compressed air is provided for actuating at least one movable valve body.
  • a control piston 107i influenced by the pressure of the compressed air is provided for actuating at least one movable valve body.
  • the compressed air outlet valve 54i in this case is not designed as a plate valve but as a slide valve, the valve closing part 65i, which is cuffed in the manner of an annular sealing lip, being provided as a valve slide on the outer circumference of the control piston 107i and in and out of the area of valve slots on an inner circumferential surface of the ring gap for the valve spring 66i including the compressed air duct 90i is movable.
  • the valve slots 109 can be provided in a simple manner on the collar-shaped casing of the insert 64i.
  • the annular control piston 107i from which the valve closing part 65i protrudes in the direction of the pressure chamber, is displaced against the force of the valve spring 66i in such a way that the sealing lip of the valve closing part 65i moves from a valve slot-free area into the area of the valve slots 109 arrives so that the compressed air can pass from the compressed air chamber into the compressed air channel 90i.
  • the control device 106i or the control piston 107i actuates a further air closing valve 110, for which a further, correspondingly cuff-shaped and protruding valve closing part 111, similar to the valve closing part 65i, is provided on the inner circumference of the control piston 107i.
  • This valve closing part 111 is assigned at least one or a ring of uniformly distributed valve openings 112 on an outer circumferential surface, these valve openings 112 being provided in a simple manner in the sleeve part of the insert 64i in the form of radial bores and in an annular channel between the associated end of the piston shaft 21i and this Sleeve part and from there into the media channel section 88i open.
  • the compressed air outlet valve 54i and the slide closing valve 110 are closed by the associated valve closing parts 65i, 111.
  • the control piston 107i Under the increasing compressed air overpressure, the control piston 107i is first moved over a partial path and the air closing valve 110 is thereby opened, so that the compressed air flows into the liquid path or into the channel section 88i. Since the compressed air in this case strikes the liquid conveyed into the media channel section 88i at the same time, there is a backflow and, if appropriate, also due to the rising in the compressed air chamber Pressure, the control piston 107i is moved further against the force of the valve spring 66i, so that now the compressed air outlet valve 65i, which is initially still closed, opens and the compressed air can flow to the channel section 89i.
  • the outlet valve 54i closes as a result of the lack of back pressure or back pressure in that the control piston 107i now moves back by the corresponding partial path.
  • the closing valve 110 remains open, so that the air, which is still under pressure in the compressed air chamber, flows into the associated liquid paths or channel sections and cleans them, including the discharge nozzle 25i. It is also conceivable to control this reversal mechanically or depending on the path.
  • the individual components of the discharge device for example the respective pumps, their components, the valves, the control devices, also represent themselves as well as the discharge nozzles feature combinations essential to the invention.

Landscapes

  • Nozzles (AREA)
  • Coating Apparatus (AREA)
  • Closures For Containers (AREA)
  • Reciprocating Pumps (AREA)
  • Catching Or Destruction (AREA)
  • Containers And Packaging Bodies Having A Special Means To Remove Contents (AREA)
  • Electrical Discharge Machining, Electrochemical Machining, And Combined Machining (AREA)
  • Feeding And Guiding Record Carriers (AREA)
  • Details Of Reciprocating Pumps (AREA)
EP88201492A 1987-07-08 1988-07-05 Distributeur manuel pour fluide Expired - Lifetime EP0309010B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE3722469 1987-07-08
DE19873722469 DE3722469A1 (de) 1987-07-08 1987-07-08 Handbetaetigbare austragvorrichtung fuer medien
DE19873722470 DE3722470A1 (de) 1987-07-08 1987-07-08 Handbetaetigbare austragvorrichtung fuer medien

Publications (2)

Publication Number Publication Date
EP0309010A1 true EP0309010A1 (fr) 1989-03-29
EP0309010B1 EP0309010B1 (fr) 1996-02-14

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ID=25857328

Family Applications (4)

Application Number Title Priority Date Filing Date
EP88905807A Pending EP0366695A1 (fr) 1987-07-08 1988-07-05 Distributeur manuel de milieux
EP88201604A Expired - Lifetime EP0306066B1 (fr) 1987-07-08 1988-07-05 Dispositif manuel de distribution d'un fluide
EP88905806A Pending EP0365575A1 (fr) 1987-07-08 1988-07-05 Distributeur manuel de milieux
EP88201492A Expired - Lifetime EP0309010B1 (fr) 1987-07-08 1988-07-05 Distributeur manuel pour fluide

Family Applications Before (3)

Application Number Title Priority Date Filing Date
EP88905807A Pending EP0366695A1 (fr) 1987-07-08 1988-07-05 Distributeur manuel de milieux
EP88201604A Expired - Lifetime EP0306066B1 (fr) 1987-07-08 1988-07-05 Dispositif manuel de distribution d'un fluide
EP88905806A Pending EP0365575A1 (fr) 1987-07-08 1988-07-05 Distributeur manuel de milieux

Country Status (12)

Country Link
US (2) US5110052A (fr)
EP (4) EP0366695A1 (fr)
JP (2) JP2841202B2 (fr)
KR (1) KR970009563B1 (fr)
AT (2) ATE89195T1 (fr)
AU (2) AU622620B2 (fr)
CA (2) CA1337721C (fr)
DE (4) DE3722469A1 (fr)
ES (1) ES2083362T3 (fr)
RU (2) RU2067896C1 (fr)
WO (2) WO1989000086A1 (fr)
ZA (1) ZA884905B (fr)

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US10370177B2 (en) * 2016-11-22 2019-08-06 Summit Packaging Systems, Inc. Dual component insert with uniform discharge orifice for fine mist spray
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FR2397341A1 (fr) * 1977-07-12 1979-02-09 Oreal Recipient destine a la distribution d'un liquide pulverise avec injection de gaz additionnel
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Cited By (18)

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Publication number Priority date Publication date Assignee Title
FR2656900A1 (fr) * 1990-01-10 1991-07-12 Oreal Pompe manuelle a precompression pour la pulverisation d'un liquide, notamment d'un parfum.
EP0437131A1 (fr) * 1990-01-10 1991-07-17 L'oreal Pompe manuelle à précompression pour la pulvérisation d'un liquide, notamment d'un parfum
US5323936A (en) * 1990-09-01 1994-06-28 Ing. Erich Pfeiffer Gmbh & Co. Kg Media dispenser for dispensing a dosed medium in a gas flow
FR2677617A1 (fr) * 1991-06-17 1992-12-18 Oreal Dispositif pour la pulverisation d'un liquide susceptible de durcir en sechant, en particulier d'une laque, et bouton-poussoir pour un tel dispositif.
EP0519779A1 (fr) * 1991-06-17 1992-12-23 L'oreal Dispositif pour la pulvérisation d'un liquide susceptible de durcir en séchant, en particulier d'une laque
FR2684081A1 (fr) * 1991-11-26 1993-05-28 Oreal Pompe pour la distribution d'un produit, liquide ou pateux, et recipient distributeur equipe d'une telle pompe.
EP0544549A1 (fr) * 1991-11-26 1993-06-02 L'oreal Pompe pour la distribution d'un produit, liquide ou pâteux, et récipient distributeur équipé d'une telle pompe
FR2688714A1 (fr) * 1992-03-20 1993-09-24 Oreal Distributeur de liquide equipe d'une pompe de distribution et pompe de distribution pour un tel distributeur.
EP0561696A1 (fr) * 1992-03-20 1993-09-22 L'oreal Buse de distribution
FR2688711A1 (fr) * 1992-03-20 1993-09-24 Oreal Buse de distribution.
EP0561666A1 (fr) * 1992-03-20 1993-09-22 L'oreal Distributeur de liquide équipé d'une pompe de distribution et pompe de distribution pour un tel distributeur
US5397059A (en) * 1992-03-20 1995-03-14 L'oreal Dispenser equipped with a liquid pump and a pressurized gas/liquid nozzle
WO1994027758A1 (fr) * 1993-05-29 1994-12-08 Carnaudmetalbox Plc Anneau d'ecartement pour alimentation en liquide de refroidissement
GB2292901A (en) * 1993-05-29 1996-03-13 Metal Box Plc Coolant spacer ring
FR2708908A1 (fr) * 1993-08-11 1995-02-17 Oreal Bouton-poussoir à buse de pulvérisation destiné à être monté sur un distributeur et distributeur équipé d'un tel bouton-poussoir.
WO1995007763A1 (fr) * 1993-09-15 1995-03-23 Siemens & Co. Gmbh & Co. Kg Procede et dispositif de production d'aerosol
DE19813078A1 (de) * 1998-03-25 1999-09-30 Pfeiffer Erich Gmbh & Co Kg Spender für Medien sowie Verfahren zur Herstellung eines Spenders
US6257461B1 (en) 1998-03-25 2001-07-10 Ing. Erich Pfeiffer Gmbh Media dispenser having parts with shear faces for facilitating assembly

Also Published As

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RU2067896C1 (ru) 1996-10-20
ES2083362T3 (es) 1996-04-16
AU1990288A (en) 1989-01-30
EP0365575A1 (fr) 1990-05-02
ZA884905B (en) 1989-03-29
DE3722469A1 (de) 1989-01-19
KR970009563B1 (ko) 1997-06-14
WO1989000085A1 (fr) 1989-01-12
AU2072188A (en) 1989-01-30
AU622620B2 (en) 1992-04-16
JPH02504599A (ja) 1990-12-27
JP2841202B2 (ja) 1998-12-24
EP0306066A1 (fr) 1989-03-08
AU619200B2 (en) 1992-01-23
CA1336972C (fr) 1995-09-12
ATE89195T1 (de) 1993-05-15
RU2032482C1 (ru) 1995-04-10
WO1989000086A1 (fr) 1989-01-12
DE3855004D1 (de) 1996-03-28
EP0306066B1 (fr) 1993-05-12
EP0309010B1 (fr) 1996-02-14
DE3722470A1 (de) 1989-01-19
KR890701225A (ko) 1989-12-19
JPH02504007A (ja) 1990-11-22
EP0366695A1 (fr) 1990-05-09
DE3880934D1 (fr) 1993-06-17
US5147087A (en) 1992-09-15
JP2841203B2 (ja) 1998-12-24
US5110052A (en) 1992-05-05
CA1337721C (fr) 1995-12-12
ATE134166T1 (de) 1996-02-15

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