EP0532822A1 - Ausgabeeinrichtung - Google Patents

Ausgabeeinrichtung Download PDF

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Publication number
EP0532822A1
EP0532822A1 EP92102399A EP92102399A EP0532822A1 EP 0532822 A1 EP0532822 A1 EP 0532822A1 EP 92102399 A EP92102399 A EP 92102399A EP 92102399 A EP92102399 A EP 92102399A EP 0532822 A1 EP0532822 A1 EP 0532822A1
Authority
EP
European Patent Office
Prior art keywords
channel
product
output
output device
section
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.)
Withdrawn
Application number
EP92102399A
Other languages
German (de)
English (en)
French (fr)
Inventor
Franz Zimmerhackel
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.)
Deutsche Prazisions-Ventil GmbH
Deutsche Prazisions Ventil GmbH
Original Assignee
Deutsche Prazisions-Ventil GmbH
Deutsche Prazisions Ventil 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 Deutsche Prazisions-Ventil GmbH, Deutsche Prazisions Ventil GmbH filed Critical Deutsche Prazisions-Ventil GmbH
Publication of EP0532822A1 publication Critical patent/EP0532822A1/de
Withdrawn legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65D—CONTAINERS FOR STORAGE OR TRANSPORT OF ARTICLES OR MATERIALS, e.g. BAGS, BARRELS, BOTTLES, BOXES, CANS, CARTONS, CRATES, DRUMS, JARS, TANKS, HOPPERS, FORWARDING CONTAINERS; ACCESSORIES, CLOSURES, OR FITTINGS THEREFOR; PACKAGING ELEMENTS; PACKAGES
    • B65D83/00—Containers or packages with special means for dispensing contents
    • B65D83/14—Containers or packages with special means for dispensing contents for delivery of liquid or semi-liquid contents by internal gaseous pressure, i.e. aerosol containers comprising propellant for a product delivered by a propellant
    • B65D83/44—Valves specially adapted therefor; Regulating devices
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B05—SPRAYING OR ATOMISING IN GENERAL; APPLYING FLUENT MATERIALS TO SURFACES, IN GENERAL
    • B05B—SPRAYING APPARATUS; ATOMISING APPARATUS; NOZZLES
    • B05B1/00—Nozzles, spray heads or other outlets, with or without auxiliary devices such as valves, heating means

Definitions

  • the invention relates to a dispensing device for spray cans filled with a fluid product under gas pressure, with a product path that can be closed by a dispensing valve and has a throttle nozzle arrangement that has on its input side at least one input channel arranged essentially in a plane running perpendicular to the axial direction and on its output side has an essentially axially extending output channel into which the input channel opens essentially tangentially.
  • the throttle nozzle arrangement also forms an output nozzle through which the product emerges from the spray can into the environment and is sprayed or atomized.
  • the known dispensing device is used in particular where the product and the propellant gas in the interior of the spray can in one Space, but essentially separate from each other, ie the gas is not at all dissolved in the product or only with a negligibly small proportion. In such cases, the gas pressure decreases as the spray can empties. However, as the pressure decreases, the volume flow of the dispensed product also typically decreases and the droplet size of the sprayed product changes. This disadvantageous behavior can be weakened by the known throttle nozzle arrangement. The volume flow and droplet size remain largely constant, even if the pressure drops as the spray can empties.
  • the throttle nozzle arrangement causes the greatest throttling of the outflowing product. Their flow cross-section is smaller than each of the preceding restrictors. Accordingly, the greatest pressure drops through the dispensing nozzle. This makes fine adjustment of the output volume flow very difficult. If the throttle resistance is selected too high, effective spraying of the product can no longer be guaranteed. If it is chosen too small, the constancy of the volume flow can no longer be guaranteed. In addition, it is extremely difficult, particularly in the case of resinous or adhesive products which cure in conjunction with components of the air, for example oxygen, to continue to operate the known dispenser with the same properties after the product has been dispensed. As a rule, the throttle nozzle arrangement is blocked.
  • the invention is based on the object of specifying an output device which is simple to manufacture and which provides better controllability of the output volume flow.
  • This arrangement not only ensures that the throttle nozzle arrangement is largely sealed off from the ambient atmosphere, that is, components of this atmosphere cannot carry out any chemical processes with the product which could lead to the throttle nozzle arrangement sticking together. It is also achieved that the volume flow is much more controllable.
  • the initial product flow which in the known case is approximately 0.55 g / s, can be reduced to approximately 0.3 g / s with the output device according to the invention, this value being maintained with slight changes over the entire emptying of the spray can can. In addition, the production of such an output device is much easier.
  • the throttle nozzle arrangement can be built into the product path in a quasi self-retaining manner.
  • an expansion space is provided between the throttle nozzle arrangement and the dispensing valve.
  • the flow velocity of the product flowing into this expansion space is largely reduced by the throttle nozzle arrangement, in which the product has not only been throttled, but also swirled due to the tangential entry ducts opening into the outlet duct, the flow velocity being significantly less strong due to the special design of the throttle nozzle arrangement depends on the pressure difference across the throttle nozzle arrangement than with simple throttles.
  • the expansion in the expansion space is followed by a further throttling in the dispensing valve. If necessary, further expansion and subsequently further throttling through an outlet nozzle is possible.
  • the outflow speed of the product i.e. the volume flow, is mainly determined by the structure and dimensioning of the throttle nozzle arrangement.
  • the size of the expansion space changes when the dispensing valve is actuated, in particular reduced. This allows a further, very sensitive control of the product flow to be achieved.
  • the dispensing valve can generally be opened more or less, which results in different pressure conditions in the expansion space, which are also dependent on the volume flow of the product flowing out. The changes in this pressure ratio can be partially compensated for by changing the size of the expansion space. Complete compensation is not desirable, however, since a differently large opening of the dispensing valve is also used to achieve a different outflow rate of the product.
  • the input channel advantageously has a reduced cross-section in the region of its mouth into the output channel.
  • This reduction in cross section leads to an acceleration of the product flowing through the throttle nozzle arrangement just at the moment when the product flows into the outlet channel.
  • the tangential inflow creates a swirl in the outlet channel. The greater the inflow speed, the more intense the swirl can be.
  • the constancy of the volume flow depends strongly on the strength of the turbulence and the better the greater the turbulence, the better. Therefore, the narrowing of the cross-section further ensures that the volume flow can be kept constant.
  • the cross section of the input channel continuously decreases in the direction of the output channel. This accelerates the product relatively evenly.
  • the throttle nozzle arrangement preferably has an insert part which is inserted into the product path and has a continuous outlet channel and an inlet channel which is at least partially open towards the inlet side and abuts against a stop in the outlet path, the stop covering the outlet channel on the inlet side and leaving part of the inlet channel free.
  • the throttle nozzle arrangement is thus essentially formed by two parts, namely the insert and the stop.
  • the stop not only serves as a mechanical support for the insert. It also prevents the product from flowing freely through the exit channel. Rather, it forces the product to flow tangentially into the output channel through the input channel or channels, which it leaves partially free, in order to be swirled there. Due to the separate insert part, the production of the output device can be made very simple.
  • the product channel has a circular cross section or a cross section in the form of a regular polygon at least in the region of the insert part and the cross section of the insert part is adapted to the cross section of the product channel.
  • the insert can therefore be used in practically any angular position. It is not necessary to pay attention to certain directions of use.
  • the insert part preferably has a disk containing the insert channel and the outlet channel, which is arranged essentially perpendicular to the axis of the product channel within a hollow cylinder.
  • the insert part thus has the shape of an H in cross-section, the crossbeam of the H representing the disk and the four branches of the H representing the wall of the hollow cylinder. This shape allows the insert to be sealed well in the product channel without the need for costly measures. The product is forced to flow through the orifice assembly without being able to flow past it to the side. The production of such an insert is very simple.
  • the hollow cylinder preferably widens conically on the output side. This not only has positive properties on the flow behavior of the product as it exits the outlet channel, the taper also enables the return spring to be guided laterally safely and centered with respect to the insert.
  • the disc has grooves or webs on the output side, which run outwards, in particular radially, from the output channel and are connected to axial grooves or axial webs provided in the inner wall of the hollow cylinder. Even if the actuator of the output valve is pressed down so far that it comes to rest on the disc, a product flow is guaranteed, whereby through the grooves on the disc and the axial grooves in the inner wall of the hollow cylinder or the spaces between the webs on the disc or a suitable flow path is formed on the axial webs on the inner wall of the hollow cylinder. When using axial webs, it is sufficient if the diameter space delimited by the axial webs widens conically.
  • the wall thickness of the hollow cylinder is advantageously essentially constant in the area of the axial grooves or in the area between the axial webs.
  • the depth of the axial grooves or the thickness of the axial webs thus decreases in the direction of the exit side of the insert. This allows a gradual transition of the escaping product from the axial grooves into the expansion space.
  • the hollow cylinder preferably has a wall thickness at the outlet end which corresponds to that in the region of the axial grooves or in the region between the axial webs.
  • a smooth surface results directly at the edge of the hollow cylinder, through which the product can flow into the expansion space.
  • the length of the hollow cylinder is preferably at least equal to its radius. This ensures sufficient stability of the hollow cylinder in the product channel. Tilting or tilting of the insert during assembly is largely excluded.
  • the output channel has a section with a smaller diameter, into which the input channel opens, and a section with a larger diameter. You can make a relatively precise adjustment of the size of the volume flow by changing the lengths of these two sections. The rest of the shape of the insert does not have to be changed. This makes production very easy. Only parts of an injection mold need to be replaced, but not the entire mold must be replaced.
  • An output device 1 is arranged in a lid 2 of a spray can, not shown. It has a housing 3 in which a valve member 4 of a dispensing valve 5 is displaceably arranged against the force of a return spring 6.
  • the dispensing valve 5 closes a product path 14 or releases it when actuated.
  • the valve member 4 has one or more transverse channels 7. When the return spring 6 has moved the valve member 4 into the rest position 8 shown, the transverse channels 7 are closed by a seal. If the valve member 4 has been pressed into the housing 3 against the force of the return spring 6, the transverse channels 7 open into an annular space 9 which surrounds the valve member 4 within the housing 3.
  • the annular space 9 opens into an expansion space 10 which is delimited on the opposite side by a throttle nozzle arrangement 11.
  • the throttle nozzle arrangement has an insert part 12 which bears against a stop 13 which is provided in the product channel 14 and is connected, for example, to the wall of the product channel 14 via one or more webs 15. At the inlet end of the product channel 14 there is a riser 16 through which a product can be supplied from the spray can. Furthermore, a circumferential projection 29 is provided in the product channel 14, behind which the insert part 12 engages. The projection 29 can also be interrupted. The insert is clamped between the projection 29 and the stop 13.
  • the product in the spray can is under pressure from a gas that is not dissolved in the product. With increasing emptying of the spray can, the space available for this gas becomes ever larger. As a result, the pressure of the gas decreases.
  • the throttle nozzle arrangement 11 arranged in the product channel 14 ensures in particular in Connection to the expansion space 10 so that the volume flow of the product can be kept at least approximately constant despite the decrease in gas pressure in the container, ie the output speed of the product is largely independent of the emptying state of the can.
  • the insert part 12 of the throttle nozzle arrangement 11 has the shape of an H in cross section, the transverse strut of the H being formed by a disk 17 which is arranged within a hollow cylinder 18.
  • the disk is delimited by two flat surfaces 19, 20 which run essentially parallel to one another.
  • the hollow cylinder 18 widens conically on the output side, i.e. its wall thickness decreases starting from the disk 17 towards the outlet side in the direction of the dispensing valve 5.
  • the hollow cylinder 18 has a rounded portion 21 at its input end, via which the outer wall of the hollow cylinder 18 merges into its end face.
  • the hollow cylinder 18 has a greater wall thickness on the input side than on the output side.
  • the length of the hollow cylinder 18 corresponds at least to the radius. As a rule, however, it is larger. It can also be in the region of twice the radius.
  • An output channel 22 is arranged in the disk 17 of the insert part 12. This output channel 22 passes through the disc 17 completely.
  • the outlet channel has a section 22a with a smaller diameter and a section 22b with a larger diameter as well as a swirling space 25 upstream of section 22a.
  • three rotatingly symmetrical open Input channels 23, which are arranged on the input side of the disk 17 of the insert part 12, that is to say the side which faces away from the dispensing valve 5.
  • the input channels 23 are open towards the input side, ie they are groove-like in the surface 20. They extend from the wall of the hollow cylinder 18 to the outlet channel 22, wherein they are designed such that they open tangentially into the outlet channel 22.
  • a flow of the product directed through the inlet channels 23 is therefore forced to swirl in the outlet channel 22, ie in the swirling space 25.
  • a flow then prevails in the outlet channel 22, which has an essential component in the azimuthal direction. This component can be larger than the flow component in the axial direction.
  • the input channels 23 have at their end facing the output channel 22 a reduction in cross section 24, which is formed in that the cross section of the input channels 23 in the direction of the output channel 22 is continuously reduced.
  • the input channels 23 do not run exactly radially, but run from the wall of the hollow cylinder 18 to a point which is offset outwards from the center of the disk 17 by a predetermined amount.
  • radially extending webs 26 or projections are arranged on the surface 19 of the disk 17, which extend in axial webs 27 on the wall of the hollow cylinder 18.
  • a space remains between the webs 26.
  • the wall thickness of the hollow cylinder 18 is constant.
  • the wall thickness of the axial webs 27 decreases continuously from the disk 17 to the end on the output side until it has a thickness at the end of the insert part 12 which corresponds to that in the region between the axial webs 27.
  • radially extending grooves 26 ' are arranged on the output side in the surface 19' of the disk 17, which grooves open into axial grooves 27 'in the wall of the hollow cylinder 18'.
  • the wall thickness of the hollow cylinder 18' is constant. Outside the axial grooves 27 ', the wall thickness decreases continuously from the disk 17 towards the output end until it reaches a thickness at the output end of the insert part 12 which corresponds to the constant thickness in the region of the axial grooves 27'.
  • a product path is ensured by the grooves or the spaces between the webs, even if the valve member 4 is pressed in very far.
  • the expansion space 10 is when the valve member 4 is depressed, i.e. when opening the output valve 5, downsized. The more the valve member 4 is depressed, i.e. the further the discharge valve 5 is opened, the greater the reduction in the expansion space 10.
  • partial compensation can be achieved in that the volume flow increases to a lesser extent than this would normally be expected when the valve member 4 is actuated. This allows a very fine and sensitive control of the volume flow when the valve 4 is actuated. Even if the valve member 4 is moved so far against the force of the return spring 6 towards the insert part 12 that it comes to rest there, a flow path for the fluid is ensured by the grooves 26 'or the webs 26.
  • the axial grooves 27 'and the axial webs 27 on the one hand ensure an interruption of the smooth surface of the hollow cylinder 18, as a result of which the component of the flow of the product in the azimuthal direction is reduced after leaving the outlet channel 22, and on the other hand the hollow cylinder 18 has a smooth end on the outlet side Edge on, so that no additional swirls arise when leaving the hollow cylinder 18.
  • a centering of the return spring 6 in the insert part 12 is achieved by the taper of the hollow cylinder 18 or the axial webs 27. Since the insert 12, like the product channel 14, has a circular cross section, the insert 12 can be inserted into the product channel 14 in any angular position. The assembly is further facilitated by the rounding 21.
  • the throttle property of the throttle nozzle arrangement 11 can be controlled with very simple measures via the two sections 22a, 22b of the outlet channel 22.
  • the flow resistance increases. If it is reduced, it will decrease. On the other hand, nothing needs to be changed in the remaining shape of the insert part 12.
  • the production of the output device 1 is very simple. It differs from the production of a conventional output device only in that the insert part 12 must also be inserted into the product channel 14. Due to the rounding 21 and the circular cross-sectional shape of the insert 12, this additional work step is very simple, so that it practically does not adversely affect production.

Landscapes

  • Chemical & Material Sciences (AREA)
  • Dispersion Chemistry (AREA)
  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Containers And Packaging Bodies Having A Special Means To Remove Contents (AREA)
  • Nozzles (AREA)
EP92102399A 1991-09-16 1992-02-13 Ausgabeeinrichtung Withdrawn EP0532822A1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4130728A DE4130728A1 (de) 1991-09-16 1991-09-16 Ausgabeeinrichtung
DE4130728 1991-09-16

Publications (1)

Publication Number Publication Date
EP0532822A1 true EP0532822A1 (de) 1993-03-24

Family

ID=6440696

Family Applications (1)

Application Number Title Priority Date Filing Date
EP92102399A Withdrawn EP0532822A1 (de) 1991-09-16 1992-02-13 Ausgabeeinrichtung

Country Status (12)

Country Link
EP (1) EP0532822A1 (ja)
JP (1) JPH0662184B2 (ja)
KR (1) KR930005680A (ja)
CN (1) CN1074991A (ja)
AU (1) AU649791B2 (ja)
BR (1) BR9200968A (ja)
CA (1) CA2062863A1 (ja)
DE (1) DE4130728A1 (ja)
HU (1) HUT62525A (ja)
MX (1) MX9201268A (ja)
NZ (1) NZ244350A (ja)
ZA (1) ZA922043B (ja)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4836018A (en) * 1988-10-17 1989-06-06 Charles Dispenza Rain gauge with improved syphon discharge
DE19850146A1 (de) * 1998-10-30 2000-05-11 Coster Tecnologie Speciali Spa Ventil für die Abgabe von unter Druck stehenden Flüssigkeiten
DE20315714U1 (de) * 2003-10-13 2003-12-18 Lindal Ventil Gmbh Kippventil zum Austragen von Schaum und anderen Medien

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2807927A1 (de) * 1977-03-02 1978-09-07 Abplanalp Robert H Ventileinheit fuer eine unter druck stehende fluessigkeits-ausgabevorrichtung und eine mit dieser ventileinheit versehene ausgabevorrichtung
US4247025A (en) * 1979-08-06 1981-01-27 Summit Packaging Systems, Inc. Aerosol valve having liquid-phase/vapor-phase mixer-homogenizer
EP0420538A1 (en) * 1989-09-27 1991-04-03 Aerosol Inventions And Development S.A.A.I.D. S.A. Pressurised dispensers

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3893597A (en) * 1973-08-20 1975-07-08 Ronald F Ewald Low delivery rate valve
IT1096119B (it) * 1978-04-13 1985-08-17 Coster Tecnologie Speciali Spa Valvola perfezionata per la miscelazione di fluidi e per l'erogazione della miscela risultante
GB8603171D0 (en) * 1986-02-08 1986-03-12 Howard A N Dietary product

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2807927A1 (de) * 1977-03-02 1978-09-07 Abplanalp Robert H Ventileinheit fuer eine unter druck stehende fluessigkeits-ausgabevorrichtung und eine mit dieser ventileinheit versehene ausgabevorrichtung
US4247025A (en) * 1979-08-06 1981-01-27 Summit Packaging Systems, Inc. Aerosol valve having liquid-phase/vapor-phase mixer-homogenizer
EP0420538A1 (en) * 1989-09-27 1991-04-03 Aerosol Inventions And Development S.A.A.I.D. S.A. Pressurised dispensers

Also Published As

Publication number Publication date
MX9201268A (es) 1993-03-01
KR930005680A (ko) 1993-04-20
HU9201039D0 (en) 1992-06-29
HUT62525A (en) 1993-05-28
JPH0662184B2 (ja) 1994-08-17
CA2062863A1 (en) 1993-03-17
ZA922043B (en) 1992-11-25
AU1282892A (en) 1993-03-18
NZ244350A (en) 1994-06-27
DE4130728A1 (de) 1993-03-18
BR9200968A (pt) 1993-04-13
JPH05213381A (ja) 1993-08-24
CN1074991A (zh) 1993-08-04
AU649791B2 (en) 1994-06-02

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