EP0109361B1 - Actuating regulator - Google Patents

Actuating regulator Download PDF

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Publication number
EP0109361B1
EP0109361B1 EP19830810512 EP83810512A EP0109361B1 EP 0109361 B1 EP0109361 B1 EP 0109361B1 EP 19830810512 EP19830810512 EP 19830810512 EP 83810512 A EP83810512 A EP 83810512A EP 0109361 B1 EP0109361 B1 EP 0109361B1
Authority
EP
European Patent Office
Prior art keywords
piston
fact
pressure
regulator according
product
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired
Application number
EP19830810512
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German (de)
French (fr)
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EP0109361A1 (en
Inventor
Winfried Jean Werding
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Individual
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Individual
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Publication date
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Priority to AT83810512T priority Critical patent/ATE21675T1/en
Publication of EP0109361A1 publication Critical patent/EP0109361A1/en
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Publication of EP0109361B1 publication Critical patent/EP0109361B1/en
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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
    • B05B1/34—Nozzles, spray heads or other outlets, with or without auxiliary devices such as valves, heating means designed to influence the nature of flow of the liquid or other fluent material, e.g. to produce swirl
    • B05B1/3405—Nozzles, spray heads or other outlets, with or without auxiliary devices such as valves, heating means designed to influence the nature of flow of the liquid or other fluent material, e.g. to produce swirl to produce swirl
    • B05B1/341—Nozzles, spray heads or other outlets, with or without auxiliary devices such as valves, heating means designed to influence the nature of flow of the liquid or other fluent material, e.g. to produce swirl to produce swirl before discharging the liquid or other fluent material, e.g. in a swirl chamber upstream the spray outlet
    • B05B1/3421—Nozzles, spray heads or other outlets, with or without auxiliary devices such as valves, heating means designed to influence the nature of flow of the liquid or other fluent material, e.g. to produce swirl to produce swirl before discharging the liquid or other fluent material, e.g. in a swirl chamber upstream the spray outlet with channels emerging substantially tangentially in the swirl chamber
    • B05B1/3431—Nozzles, spray heads or other outlets, with or without auxiliary devices such as valves, heating means designed to influence the nature of flow of the liquid or other fluent material, e.g. to produce swirl to produce swirl before discharging the liquid or other fluent material, e.g. in a swirl chamber upstream the spray outlet with channels emerging substantially tangentially in the swirl chamber the channels being formed at the interface of cooperating elements, e.g. by means of grooves
    • B05B1/3436—Nozzles, spray heads or other outlets, with or without auxiliary devices such as valves, heating means designed to influence the nature of flow of the liquid or other fluent material, e.g. to produce swirl to produce swirl before discharging the liquid or other fluent material, e.g. in a swirl chamber upstream the spray outlet with channels emerging substantially tangentially in the swirl chamber the channels being formed at the interface of cooperating elements, e.g. by means of grooves the interface being a plane perpendicular to the outlet axis
    • 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
    • B05B1/34—Nozzles, spray heads or other outlets, with or without auxiliary devices such as valves, heating means designed to influence the nature of flow of the liquid or other fluent material, e.g. to produce swirl
    • B05B1/3405—Nozzles, spray heads or other outlets, with or without auxiliary devices such as valves, heating means designed to influence the nature of flow of the liquid or other fluent material, e.g. to produce swirl to produce swirl
    • B05B1/341—Nozzles, spray heads or other outlets, with or without auxiliary devices such as valves, heating means designed to influence the nature of flow of the liquid or other fluent material, e.g. to produce swirl to produce swirl before discharging the liquid or other fluent material, e.g. in a swirl chamber upstream the spray outlet
    • B05B1/3468—Nozzles, spray heads or other outlets, with or without auxiliary devices such as valves, heating means designed to influence the nature of flow of the liquid or other fluent material, e.g. to produce swirl to produce swirl before discharging the liquid or other fluent material, e.g. in a swirl chamber upstream the spray outlet with means for controlling the flow of liquid entering or leaving the swirl chamber
    • B05B1/3473—Nozzles, spray heads or other outlets, with or without auxiliary devices such as valves, heating means designed to influence the nature of flow of the liquid or other fluent material, e.g. to produce swirl to produce swirl before discharging the liquid or other fluent material, e.g. in a swirl chamber upstream the spray outlet with means for controlling the flow of liquid entering or leaving the swirl chamber in response to liquid pressure
    • 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
    • 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
    • B65D83/16—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 characterised by the actuating means
    • B65D83/20—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 characterised by the actuating means operated by manual action, e.g. button-type actuator or actuator caps
    • 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
    • B65D83/75—Aerosol containers not provided for in groups B65D83/16 - B65D83/74
    • B65D83/753—Aerosol containers not provided for in groups B65D83/16 - B65D83/74 characterised by details or accessories associated with outlets
    • B65D83/7535—Outlet valves opened by the product to be delivered
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/7722—Line condition change responsive valves
    • Y10T137/7781—With separate connected fluid reactor surface
    • Y10T137/7784—Responsive to change in rate of fluid flow
    • Y10T137/7792—Movable deflector or choke

Definitions

  • the present invention relates to a thrust regulator according to the preamble of claim 1 in order to maintain constant at least approximately the flow rate of the product per unit of time during the expulsion of the latter out of the container, and this notwithstanding the fall of pressure which is proportional to the volume of product expelled, when the pressure source consists of a propellant such as a compressed gas, for example air or nitrogen.
  • a propellant such as a compressed gas, for example air or nitrogen.
  • the aforementioned European patent application proposes a thrust regulator, with the aid of which the flow rate per unit of time d is kept at least approximately constant.
  • a product expelled from a pressure container notwithstanding the pressure drop acting on the product inside the container.
  • This regulator has, in an evacuation channel, a differential piston, the dimension of which relative to that of the evacuation channel is such that a minimum passage section for the evacuation of the product remains at all times of the expulsion.
  • the differential piston has surfaces of different dimensions at the ends, the largest surface being opposite the flow of the product.
  • a spring which is calibrated so that under the action of a pressure of a predetermined value in the container, it is compressed in order to take up a first end-of-travel position, by which it reduces the passage section of the evacuation channel to a minimum section and that in proportion to the pressure drop in the container, following the evacuation of the product from the container, the spring expands and displaces the piston, which results in an increase progressive of the passage section of the discharge channel, until the piston reaches a second end-of-travel position, as soon as a predetermined minimum pressure settles in the container.
  • the shape of the piston relative to that of the evacuation channel is chosen so that by its movement it ensures that the product resulting from the multiplication of the pressure in the container by the passage section of the evacuation channel remains, at less approximately, constant.
  • Each of the embodiments proposed in the aforementioned European application has shortcomings and disadvantages, such as too high permeability of the membranes at vapor pressure, too high price of the parts injected in synthetic material, due to the required rigidity and regulation and consequently a jerky spraying due to an axial back and forth movement of the differential piston.
  • the object of the present invention is to propose an improved regulator which makes it possible, in common with the nozzle as described in the aforementioned US Pat. as the container is emptied of its content in the aerosol container having as propellant a compressed gas such as nitrogen or air.
  • this object is achieved by a regulator as defined in claim 1.
  • a regulator as defined in claim 1.
  • Various characteristics of this regulator are included in the subclaims.
  • a pusher 6 is provided with a cage 1 which has an evacuation channel 8a with a large diameter section 39, a medium diameter section 40 and a small diameter section 50.
  • This evacuation channel opens into a supply channel 60 for a nozzle 5 and comprises a differential piston 2, the upstream side 14 of which has a large diameter, cooperating with the section of average diameter 40 and which has a chamber 17 which serves as a fulcrum for a column of a product 18, while its downstream side 12 has a small diameter and an end 12a having an aerodynamic shape to reduce the turbulence which can be created during the evacuation of the product 18 through the evacuation channel 8a.
  • An upstream lower edge 61 of the feed channel 60 is located at a distance A from the end 12a of the differential piston, a distance which must be large enough for the turbulence which is created around the end 12a, despite its shape aerodynamic, can agglomerate, in order to reach a laminar flow of the product 18, before the latter passes the upstream lower edge 61 of the supply channel 60.
  • the small diameter section 50 of the discharge channel of the cage 1 has, opposite the inlet of the feed channel 60, a curved wall 41, intended to prevent the formation of other turbulences, for example created by angles, and to facilitate the flow of the laminar flow of the product 18 towards the nozzle 5.
  • the differential piston 2 is provided with a shoulder 15, on which a spring 3 rests, and grooves 16 and 16a, through which the product 18 can flow, even on the differential piston 2 occupies a first downstream end position in which the spring is fully compressed.
  • the shoulder 15 also serves as a stop for limiting the stroke of the differential piston 2, when the latter is moved downstream by the product 18 under the highest expulsion pressure which may prevail in the container.
  • the spring 3 expands and pushes the differential piston in the upstream direction, until it reaches a second end-of-travel position in which it is supported by a clamping sleeve 20 which is fitted on a piston 35 of an aerosol valve not shown located inside a ferrule 31.
  • the ferrule 31 On its periphery the ferrule 31 carries a chimney 53 which serves as axial guidance for a pusher 6 , in order to avoid an overly pronounced tilting of the latter.
  • a slight tilting is inevitable, because the length of the pusher 6, the only fulcrum of which is the piston 35 which cannot be guided too much for technical reasons.
  • This annoying tilting could also be limited by means of a skirt attached to the socket 20 and which covers the ferrule 31.
  • the differential piston 2 When the pusher 6 is actuated for the first time after filling the container and therefore the product 18 is expelled from the latter with the strongest pressure, the differential piston 2 is moved in the downstream direction not only by the push of the product 18, but also by a suction force, created at the inlet of the feed channel 60 by the expansion of the product under pressure and by a swirl printed on the product 18. If the spring 3 would be calibrated solely according to the pushed from product 18 and not additionally as a function of this suction force, it is too weak to overcome, at the start of regulation, these two additional forces (suction force and swirl). The differential piston would therefore remain stationary and would not move upstream.
  • Fig. 2 shows a second preferred embodiment of the regulator according to the invention, housed in the pusher 6 which serves as an opening element of a valve 25 consisting of a body 26, a seat 27, a inner seal 28, an outer seal 29, a spring 30 and the ferrule 31, a dip tube not being shown.
  • the pusher 6 has a rod 32, provided with a pipe 33, parallel to the axis of the rod 32 and a perpendicular pipe 34.
  • the rod 32 is inserted into the seat 27 of the valve 25 by way of which the seat 27 closes the inlet of the pipe 33.
  • the perpendicular pipe 34 is placed so that its inlet is normally inserted in the upper part of the joint 28.
  • This design is essential especially in cases where the regulator according to the invention is used to spray products 18, an excessive amount of which at the outlet of the nozzle 5, while drying, could obstruct it.
  • FIG. 2 shows said second embodiment of the regulator according to the invention in the rest position, the spring 3 having pushed the differential piston 2 into its starting position, while FIG. 3 illustrates the position of the differential piston 2 during use, when the valve 25, not shown, is open and the product 18 flows under the highest pressure which may prevail in the container, also not shown.
  • the regulation takes place as explained with the aid of FIG. 4, as follows: as soon as the valve 25 is opened, the product 18 penetrates on the one hand into the chamber 17 of the differential piston 2 and on the other hand flows along the latter into the evacuation channel 8a. Under the pressure of the product 18 the differential piston 2 is pushed in the direction of the nozzle 5 in reverse of the force of the spring 3 which is compressed. The front face of the small diameter section 12 of the differential piston 2 is firmly pressed against the center of a core 4 which is part of the nozzle 5 and is housed on its upstream side, so that it enters a chamber 23, the volume of which it decreases.
  • Protrusions 22 of the core 4 and a circular edge 19 of the nozzle 5 are in firm contact with the cage 1, so that the product 18 under pressure can move towards the nozzle 5 only through grooves-conduits 24 of the core 4. As these are perpendicular to the discharge channel 8a, obstructive turbulence is caused at the outlet of the grooves-pipes 24. Because the grooves-conduits 24 are tangential with respect to the chamber 23, the flow of the product 18, although turbulent, is subjected to a rotary flow, perpetuated by the circular edge 19 which transforms the turbulent flow into laminar flow which feeds finally the nozzle 5 by channels 21. Because the turbulence is transformed into laminar flow, it no longer constitutes a braking force which is all the stronger as the pressure of the high product, but without being able to reach a force blocking the flow.
  • the braking, imparted to the flow of the product 18 by the obstructive turbulence is, in this execution of the regulator, in fact an essential part of the beginning of the regulation of the flow rate per unit of time. Indeed, the spring 3 must not move from the start of the evacuation of the product 18 the differential piston 2, but only, when the thrust of the product 18 decreases to a point where the passage section for the product 18 must be enlarged , so that an unchanged amount of product 18 can reach the nozzle 4 per unit of time.
  • the rod 32 of the pusher 6 must be provided with a large diameter 32a, with which it rests on the seal 28, the perpendicular pipe 34 being immediately below the diameter 32a and not having a round, but rectangular section. Therefore, when the pusher 6 is moved downward to open the valve 25, it remains closed for longer by the seal 28 than a round pipe which, for a section of identical size must have a diameter such that part of its inlet is already disengaged from the seal 28, before the valve 25 is sufficiently open to release all the pressure, under which the product 18 is found.
  • the perpendicular pipe 34 is of rectangular section, it requires on the one hand, a path for the displacement of the pusher 6 which is larger so that its entry is clear of the seal 28 and on the other hand, instead of presenting as a entry a small part of its section, it presents almost instantaneously, but later, all of its product entry section 18 which is therefore expelled with all the pressure available, because the valve 25 is fully open, before the perpendicular pipe 34 is opened.
  • the regulator according to the invention as shown in detail in FIG. 4 is constituted by the cage 1, the differential piston 2, the spring 3 and the core 4 which can be made in one piece with the nozzle 5 and can be housed either in the pusher 6 or in a mounting cylinder 7, illustrated in fig. 6.
  • the discharge channel is formed by pipes 8, 9, 10 and 11.
  • the differential piston 2 is provided with grooves 16 and 16a.
  • the force of the spring 3 is preferably chosen so that if the product 18 is subjected to an initial pressure of 5 bar, the spring is compressed in block to allow the differential piston 2 to press firmly against the core 4.
  • the latter is preferably inserted into the nozzle 5, so that it forms with the edge 19 thereof a depression 19a, from which the supply channels 21 of the nozzle 5 start.
  • the upstream face of the core 4 carries the protuberances 22 and are center presents the chamber 23, from which leave the grooves-conduits 24, each of which forms tangent with the circumference of the chamber 23.
  • the upstream face of the protrusions 22 and the circular edge 19 of the nozzle 5 are in firm contact with the cage 1 , so that the grooves-conduits 24 become reellement of the conduits which connect the chamber 23 to the recess 19a which thus becomes an annular conduit from which the product 18 is introduced into the supply channels 21 of the nozzle 5.
  • FIG. 7 The regulation of the flow using the regulator according to the invention is illustrated in FIG. 7, the line 45 of which represents the flow of product 18 per unit of time, when a commercial nozzle is used, while the line 36 shows the flow per unit of time, obtained when a nozzle is used according to the American patent No. 4,260,110 alone.
  • Line 37 illustrates the flow rate per time unit obtained by using the regulator according to the invention in common with the aforementioned nozzle.

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  • 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)
  • Organic Low-Molecular-Weight Compounds And Preparation Thereof (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Diaphragms For Electromechanical Transducers (AREA)
  • Steering Control In Accordance With Driving Conditions (AREA)
  • Safety Valves (AREA)
  • Magnetic Bearings And Hydrostatic Bearings (AREA)

Description

La présente invention a pour objet un régulateur de poussée selon le préambule de la revendication 1 afin de maintenir constant au moins approximativement le débit du produit par unité de temps lors de l'expulsion de ce dernier hors du récipient, et cela nonobstant la chute de pression qui est proportionnelle au volume de produit expulsé, lorsque la source de pression est constituée par un agent propulsif tel qu'un gaz comprimé, par exemple de l'air ou de l'azote.The present invention relates to a thrust regulator according to the preamble of claim 1 in order to maintain constant at least approximately the flow rate of the product per unit of time during the expulsion of the latter out of the container, and this notwithstanding the fall of pressure which is proportional to the volume of product expelled, when the pressure source consists of a propellant such as a compressed gas, for example air or nitrogen.

Un tel régulateur est connu de la demande de brevet européenne no 81902294.8, publiée comme document WO 82/00450.Such a regulator is known from European patent application No. 81902294.8, published as document WO 82/00450.

Dans un récipient ou un flacon aérosol la poussée résulte de la pression qui agit sur la surface du produit à l'intérieur du récipient. Afin de la tenir plus ou moins constante pendant toute la durée d'utilisation du récipient, on s'est servi d'hydrocarbures chlorofluorés du type Fréon comme agent propulsif des aérosols. Pour contribuer à la protection de la ceinture d'ozone qui protège notre globe contre un rayonnement ultra-violet excessif, de nombreux pays interdisent cependant l'utilisation de tels agents propulsifs.In an aerosol container or bottle the pressure results from the pressure which acts on the surface of the product inside the container. In order to keep it more or less constant throughout the period of use of the container, chlorofluorinated hydrocarbons of the Freon type have been used as propellant for aerosols. To contribute to the protection of the ozone belt which protects our globe against excessive ultraviolet radiation, many countries however prohibit the use of such propellants.

Dès lors on a de plus en plus recours aux mélanges propane-butane ou à l'éther diméthylique comme agents propulsifs. Si le Fréon est dange- . reux pour l'environnement, le propane-butane et l'éther diméthylique constituent un danger par leur caractère explosif.Consequently, use is increasingly made of propane-butane mixtures or of dimethyl ether as propellants. If the Freon is dangerous. rous for the environment, propane-butane and dimethyl ether constitute a danger by their explosive nature.

On a essayé d'utiliser du C02, N2, N20 ou simplement de l'air comprimé comme agent propulsif. L'utilisation de ces gaz se heurte cependant au fait qu'au fur et à mesure de l'expulsion du produit du récipient il en résulte, par l'augmentation du volume restant dans le récipient, une chute de pression, proportionnelle à cette augmentation, et par conséquence une diminution du débit par unité de temps. De plus, si le produit est pulvérisé, on constate en même temps une augmentation de la dimension des gouttelettes, de sorte à ce que le spray devient de plus en plus mouillé, ce qui est inacceptable, tout au moins pour certaines applications. Il faut aussi éviter l'utilisation de C02 et de N20, parce que ces gaz sont partiellement absorbés par le produit à pulvériser, qui de ce fait sont expulsés avec celui-ci, ce qui provoque un débit résiduel sous forme de gouttes, après la fermeture de la valve. Ces problèmes peuvent partiellement être résolus par l'utilisation d'un gicleur tel que décrit dans le brevet USA no 4,260,110 qui permet de pulvériser finement des produits avec une faible pression purement mécanique, donc sans aucun gaz propulsif connu qui, par sa force d'expansion sous pression atmosphérique, fait exploser les gouttelettes lorsqu'elles sortent de la buse. Dans ce gicleur connu c'est uniquement le «mechanical break-up» qui assure, même avec des pressions inférieures à 2 bar, une bonne pulvérisation.We tried to use C0 2 , N 2 , N 2 0 or simply compressed air as a propellant. However, the use of these gases comes up against the fact that, as the product is expelled from the container, this results in a pressure drop proportional to this increase, by increasing the volume remaining in the container. , and consequently a decrease in the flow rate per time unit. In addition, if the product is sprayed, there is at the same time an increase in the size of the droplets, so that the spray becomes more and more wet, which is unacceptable, at least for certain applications. The use of C0 2 and N 2 0 should also be avoided, because these gases are partially absorbed by the product to be sprayed, which are therefore expelled with it, which causes a residual flow in the form of drops. , after closing the valve. These problems can partially be solved by the use of a nozzle as described in USA patent no. 4,260,110 which allows fine spraying of products with a purely mechanical low pressure, therefore without any known propellant which, by its force of expands at atmospheric pressure, explodes droplets as they exit the nozzle. In this known nozzle it is only the “mechanical break-up” which ensures, even with pressures below 2 bar, good spraying.

Toutefois en utilisant ce gicleur avec des récipients aérosols et des gaz comprimés comme agents propulsifs, on constate un grand débit de produit par unité de temps avec pulvérisation fine lorsque le récipient est rempli au maximum et se trouve sous haute pression, et un faible débit par unité de temps avec une pulvérisation toujours fine, lorsque la pression a diminué suite à l'évacuation du produit.However, using this nozzle with aerosol containers and compressed gases as propellants, there is a large flow of product per unit of time with fine spray when the container is filled to the maximum and is under high pressure, and a low flow by unit of time with an always fine spray, when the pressure has decreased following the evacuation of the product.

Afin de résoudre ce problème de débits variables en fonction d'une chute de pression dans le récipient, la demande de brevet européenne précitée propose un régulateur de poussée, à l'aide duquel on maintient au moins approximativement constant le débit par unité de temps d'un produit expulsé d'un récipient sous pression, nonobstant la chute de pression agissant sur le produit à l'intérieur du récipient. Ce régulateur présente, dans un canal d'évacuation, un piston différentiel, dont la dimension par rapport à celle du canal d'évacuation est telle, qu'une section minimale de passage pour l'évacuation du produit subsiste à tout moment de l'expulsion. Le piston différentiel présente aux extrémités des surfaces de dimensions différentes, la surface la plus grande étant opposée au flux du produit. Il s'appuie sur un ressort qui est taré de sorte à ce que sous l'action d'une pression d'une valeur prédéterminée dans le récipient, il est comprimé afin de prendre und première position de fin de course, par laquelle il réduit la section de passage du canal d'évacuation à une section minimale et que proportionnellement à la chute de pression dans le récipient, suite à l'évacuation du produit du récipient, le ressort se détend et déplace le piston, ce qui résulte en une augmentation progressive de la section de passage du canal d'évacuation, jusqu'à ce que le piston atteint une deuxième position de fin de course, dès qu'une pression minimale prédéterminée s'installe dans le récipient. La forme du piston par rapport à celle du canal d'évacuation est choisie de sorte que par son déplacement il assure que le produit résultant de la multiplication de la pression dans le récipient par la section de passage du canal d'évacuation, demeure, au moins approximativement, constante.In order to solve this problem of variable flow rates as a function of a pressure drop in the container, the aforementioned European patent application proposes a thrust regulator, with the aid of which the flow rate per unit of time d is kept at least approximately constant. a product expelled from a pressure container, notwithstanding the pressure drop acting on the product inside the container. This regulator has, in an evacuation channel, a differential piston, the dimension of which relative to that of the evacuation channel is such that a minimum passage section for the evacuation of the product remains at all times of the expulsion. The differential piston has surfaces of different dimensions at the ends, the largest surface being opposite the flow of the product. It rests on a spring which is calibrated so that under the action of a pressure of a predetermined value in the container, it is compressed in order to take up a first end-of-travel position, by which it reduces the passage section of the evacuation channel to a minimum section and that in proportion to the pressure drop in the container, following the evacuation of the product from the container, the spring expands and displaces the piston, which results in an increase progressive of the passage section of the discharge channel, until the piston reaches a second end-of-travel position, as soon as a predetermined minimum pressure settles in the container. The shape of the piston relative to that of the evacuation channel is chosen so that by its movement it ensures that the product resulting from the multiplication of the pressure in the container by the passage section of the evacuation channel remains, at less approximately, constant.

Chacune des formes d'exécution proposées dans la demande européenne précitée présente des insuffisances et des désavantages, tels que perméabilité trop élevée des membranes à la pression vapeur, prix trop élevé des pièces injectées en matière synthétique, dû à la rigidité requise et une régulation et par conséquent une pulvérisation saccadée dû à un mouvement axial de va-et-vient du piston différentiel.Each of the embodiments proposed in the aforementioned European application has shortcomings and disadvantages, such as too high permeability of the membranes at vapor pressure, too high price of the parts injected in synthetic material, due to the required rigidity and regulation and consequently a jerky spraying due to an axial back and forth movement of the differential piston.

Le but de la présente invention est de proposer un régulateur amélioré qui permet, en commun avec le gicleur tel que décrit dans le brevet américain no 4,260,110 précité, d'obtenir un débit constant par unité de temps, nonobstant la chute de pression s'installant au fur et à mesure que le récipient est vidé de son contenu dans le récipient aérosol ayant comme agent propulsif un gaz comprimé tel que l'azote ou l'air.The object of the present invention is to propose an improved regulator which makes it possible, in common with the nozzle as described in the aforementioned US Pat. as the container is emptied of its content in the aerosol container having as propellant a compressed gas such as nitrogen or air.

Selon l'invention ce but est atteint par un régulateur tel que défini dans la revendication 1. Différentes caractéristiques de ce régulateur sont comprises dans les sous-revendications.According to the invention, this object is achieved by a regulator as defined in claim 1. Various characteristics of this regulator are included in the subclaims.

Les détails de la présente invention ressortent de la description qui suit, portant sur des exemples d'exécutions préférentielles illustrées au dessin annexé qui présente à la

  • fig. 1 une vue en coupe d'une première forme d'exécution du régulateur, réglant le débit sans avoir recours à des turbulences et placé sur une valve ouverte d'un récipient aérosol dans un poussoir muni d'un gicleur;
  • fig. 2 une vue en coupe d'une deuxième forme d'exécution du régulateur, réglant le débit à l'aide de turbulences, placé sur une valve fermée d'un récipient aérosol dans un poussoir muni d'un gicleur;
  • fig. 3 le régulateur de la fig. 2 dans le cas de la valve ouverte;
  • fig. 4 une vue en perspective partiellement en coupe sur un détail du régulateur et du gicleur selon la fig. 2;
  • fig. 5 un piston différentiel tel qu'il est utilisé dans les formes d'exécution du régulateur selon les figs. 1 et 2;
  • fig. 6 une vue éclatée en perspective d'une troisième forme d'exécution du régulateur logé dans un cylindre de montage, avec le gicleur, et à la
  • fig. 7 un diagramme qui montre l'effet de régulation du débit de produit par unité de temps obtenu par l'utilisation du régulateur selon l'invention en commun avec le gicleur selon le brevet américain no 4,260,110, comparé aux débits obtenus sans régulateur.
The details of the present invention appear from the description which follows, relating to examples of preferred embodiments illustrated in the appended drawing which presents
  • fig. 1 is a sectional view of a first embodiment of the regulator, regulating the flow rate without resorting to turbulence and placed on an open valve of an aerosol container in a pusher provided with a nozzle;
  • fig. 2 a sectional view of a second embodiment of the regulator, regulating the flow rate using turbulence, placed on a closed valve of an aerosol container in a pusher provided with a nozzle;
  • fig. 3 the regulator of fig. 2 in the case of the open valve;
  • fig. 4 a perspective view partially in section on a detail of the regulator and the nozzle according to FIG. 2;
  • fig. 5 a differential piston as used in the embodiments of the regulator according to FIGS. 1 and 2;
  • fig. 6 is an exploded perspective view of a third embodiment of the regulator housed in a mounting cylinder, with the nozzle, and at the
  • fig. 7 a diagram which shows the effect of regulating the product flow rate per time unit obtained by the use of the regulator according to the invention in common with the nozzle according to American patent no. 4,260,110, compared to the flow rates obtained without regulator.

Dans la fig. 1, un poussoir 6 est muni d'une cage 1 qui présente un canal d'évacuation 8a avec une section de grand diamètre 39, une section de diamètre moyen 40 et une section de petit diamètre 50. Ce canal d'évacuation débouche dans un canal d'alimentation 60 pour un gicleur 5 et comporte un piston différentiel 2, dont le côté amont 14 présente un grand diamètre, coopérant avec la section de diamètre moyen 40 et qui présente une chambre 17 qui sert de point d'appui a une colonne d'un produit 18, tandis que son côté aval 12 présente un petit diamètre et une extrémité 12a ayant une forme aérodynamique pour réduire les turbulences qui peuvent se créer lors de l'évacuation du produit 18 par le canal d'évacuation 8a. Un bord inférieur amont 61 du canal d'alimentation 60 se trouve situé à une distance A de l'extrémité 12a du piston différentiel, distance qui doit être suffisamment grande pour que les turbulences qui se créent autour de l'extrémité 12a, malgré sa forme aérodynamique, puissent s'agglomérer, afin d'atteindre un flux laminaire du produit 18, avant que celui-ci passe le bord inférieur amont 61 du canal d'alimentation 60. De plus, la section de petit diamètre 50 du canal d'évacuation de la cage 1 présente en face de l'entrée du canal d'alimentation 60 une paroi courbe 41, destinée à éviter la formation d'autres turbulences, par exemples crées par des angles, et à faciliter l'écoulement du flux laminaire du produit 18 vers le gicleur 5. Le piston différentiel 2 est muni d'un épaulement 15, sur lequel s'appuie un ressort 3, et de rainures 16 et 16a, par lesquelles le produit 18 peut s'écouler, même su le piston différentiel 2 occupe une première position de fin de course aval dans laquelle le ressort est comprimé à bloc. L'épaulement 15 sert aussi de butée de limitation de course du piston différentiel 2, lorsque celui-ci est déplacé en direction aval par le produit 18 sous la pression d'expulsion la plus élevée qui peut régner dans le récipient. Au fur et à mesure que baisse la pression d'expulsion, le ressort 3 se détend et pousse le piston différentiel en direction amont, jusqu'à ce qu'il atteint une deuxième position de fin de course dans laquelle il s'appuie sur une douille de serrage 20 qui se trouve adaptée sur un piston 35 d'une valve aérosol non représentée se trouvant à l'intérieur d'une ferrule 31. Sur son pourtour la ferrule 31 porte une cheminée 53 qui sert de guidage axial à un poussoir 6, afin d'éviter un basculement trop prononcé de ce dernier. Un faible basculement étant inévitable, car la longueur du poussoir 6, dont le seul point d'appui est le piston 35 qui ne peut pas être trop guidé pour des raisons techniques. On pourrait également limiter ce basculement gênant à l'aide d'une jupette solidaire de la douille 20 et qui coiffe la ferrule 31.In fig. 1, a pusher 6 is provided with a cage 1 which has an evacuation channel 8a with a large diameter section 39, a medium diameter section 40 and a small diameter section 50. This evacuation channel opens into a supply channel 60 for a nozzle 5 and comprises a differential piston 2, the upstream side 14 of which has a large diameter, cooperating with the section of average diameter 40 and which has a chamber 17 which serves as a fulcrum for a column of a product 18, while its downstream side 12 has a small diameter and an end 12a having an aerodynamic shape to reduce the turbulence which can be created during the evacuation of the product 18 through the evacuation channel 8a. An upstream lower edge 61 of the feed channel 60 is located at a distance A from the end 12a of the differential piston, a distance which must be large enough for the turbulence which is created around the end 12a, despite its shape aerodynamic, can agglomerate, in order to reach a laminar flow of the product 18, before the latter passes the upstream lower edge 61 of the supply channel 60. In addition, the small diameter section 50 of the discharge channel of the cage 1 has, opposite the inlet of the feed channel 60, a curved wall 41, intended to prevent the formation of other turbulences, for example created by angles, and to facilitate the flow of the laminar flow of the product 18 towards the nozzle 5. The differential piston 2 is provided with a shoulder 15, on which a spring 3 rests, and grooves 16 and 16a, through which the product 18 can flow, even on the differential piston 2 occupies a first downstream end position in which the spring is fully compressed. The shoulder 15 also serves as a stop for limiting the stroke of the differential piston 2, when the latter is moved downstream by the product 18 under the highest expulsion pressure which may prevail in the container. As the expulsion pressure drops, the spring 3 expands and pushes the differential piston in the upstream direction, until it reaches a second end-of-travel position in which it is supported by a clamping sleeve 20 which is fitted on a piston 35 of an aerosol valve not shown located inside a ferrule 31. On its periphery the ferrule 31 carries a chimney 53 which serves as axial guidance for a pusher 6 , in order to avoid an overly pronounced tilting of the latter. A slight tilting is inevitable, because the length of the pusher 6, the only fulcrum of which is the piston 35 which cannot be guided too much for technical reasons. This annoying tilting could also be limited by means of a skirt attached to the socket 20 and which covers the ferrule 31.

Lorsqu'on actionne le poussoir 6 pour la première fois après le remplissage du récipient et de ce fait le produit 18 est expulsé de ce dernier avec la pression la plus forte, le piston différentiel 2 est déplacé en direction aval non seulement par la poussée du produit 18, mais aussi par une force d'aspiration, créée à l'entrée du canal d'alimentation 60 par la détente du produit sous pression et par un tourbillonnement imprimé au produit 18. Si le ressort 3 serait taré uniquement en fonction de la poussé du produit 18 et non pas en plus en fonction de cette force d'aspiration, il est trop faible pour vaincre, au début de la régulation, ces deux forces aditionnelles (force d'aspiration et tourbillonnement). Le piston différentiel resterait donc stationnaire et ne se délacerait pas en direction amont. Dès que par une certaine évacuation de produit 18 la pression d'évacuation baisse, le ressort pousserait soudainement le piston différentiel 2 dans une position de régulation, qui cor- responderait à la pression résiduelle. Pour éviter une telle régulation insuffisante et afin d'obtenir un déplacement continu du piston différentiel 2 dès le début de l'expulsion du produit 18, il faut utiliser un ressort différentiel qui sur une première partie de la course de détente fournit plus de force que sur le reste de la course.When the pusher 6 is actuated for the first time after filling the container and therefore the product 18 is expelled from the latter with the strongest pressure, the differential piston 2 is moved in the downstream direction not only by the push of the product 18, but also by a suction force, created at the inlet of the feed channel 60 by the expansion of the product under pressure and by a swirl printed on the product 18. If the spring 3 would be calibrated solely according to the pushed from product 18 and not additionally as a function of this suction force, it is too weak to overcome, at the start of regulation, these two additional forces (suction force and swirl). The differential piston would therefore remain stationary and would not move upstream. As soon as by a certain evacuation of product 18 the evacuation pressure drops, the spring would suddenly push the differential piston 2 into a regulation position, which would correspond to the residual pressure. To avoid such insufficient regulation and in order to obtain a continuous displacement of the differential piston 2 from the start of the expulsion of the product 18, it is necessary to use a differential spring which on a first part of the expansion stroke provides more force than for the rest of the race.

La fig. 2 montre une deuxième forme d'exécution préférentielle du régulateur selon l'invention, logée dans le poussoir 6 qui sert d'élément d'ouverture d'une valve 25 constituée d'un corps 26, d'un siège 27, d'un joint intérieur 28, d'un joint extérieur 29, d'un ressort 30 et de la ferrule 31, un tube plongeur n'étant pas représenté. Le poussoir 6 présente une tige 32, munie d'une conduite 33, parallèle à l'axe de la tige 32 et une conduite perpendiculaire 34. La tige 32 est insérée dans le siège 27 de la valve 25 de sort que le siège 27 obture l'entrée de la conduite 33. La conduite perpendiculaire 34 est placée de sorte que son entrée se trouve normalement insérée dans la partie supérieure du joint 28. Cette disposition des conduites 33 et 34 s'est imposée du fait qu'aucune valve aérosol du commerce expérimentée n'est étanche immédiatement après la fermeture, après usage. Lorsque l'agent propulsif est un gaz soluble, comme le Fréon par exemple, il y a une pulvérisation pratiquement instantanée du produit 18 à la sortie du gicleur 5 et l'écoulement du produit après la fermeture de la valve 25 s'effectue sans problème. Mais lorsqu'on utilise comme agent propulsif du gaz comprimé tel que de l'air ou l'azote, ainsi que préconisé pour le régulateur selon l'invention, le produit expulsé ne contient aucun agent qui, par sa force d'expansion sous pression atmosphérique, ferait pulvériser instantanément le produit qui s'écoule encore de la valve 25, même après sa fermeture, de sorte que l'on constate au niveau du gicleur 5 un écoulement non pulvérisé de produit qui peut durer jusqu'à vingt secondes après la fermeture de la valve 25. Cet écoulement gênant est éliminé par la disposition précitée des conduites 33 et 34 du poussoir 6 et non pas par le fait que la valve 25 est devenue étanche. L'entrée de la conduite perpendiculaire 34 étant placée dans le joint 28, ce dernier l'obture et ne permet plus au produit 18, s'écoulant encore dans le siège 27, de pénétrer dans la conduite perpendiculaire 34. La conduite 33 est, comme déjà décrit, obturée par le joint 28.Fig. 2 shows a second preferred embodiment of the regulator according to the invention, housed in the pusher 6 which serves as an opening element of a valve 25 consisting of a body 26, a seat 27, a inner seal 28, an outer seal 29, a spring 30 and the ferrule 31, a dip tube not being shown. The pusher 6 has a rod 32, provided with a pipe 33, parallel to the axis of the rod 32 and a perpendicular pipe 34. The rod 32 is inserted into the seat 27 of the valve 25 by way of which the seat 27 closes the inlet of the pipe 33. The perpendicular pipe 34 is placed so that its inlet is normally inserted in the upper part of the joint 28. This arrangement of the lines 33 and 34 imposed themselves because no aerosol valve on the market tested is leaktight immediately after closing, after use. When the propellant is a soluble gas, such as Freon for example, there is an almost instantaneous spraying of the product 18 at the outlet of the nozzle 5 and the flow of the product after closing the valve 25 is carried out without problem . But when compressed gas such as air or nitrogen is used as propellant, as recommended for the regulator according to the invention, the product expelled does not contain any agent which, by its force of expansion under pressure atmospheric, would instantly spray the product still flowing from the valve 25, even after it is closed, so that there is an unsprayed flow of product at the nozzle 5 which can last up to twenty seconds after the closing the valve 25. This annoying flow is eliminated by the aforementioned arrangement of the lines 33 and 34 of the pusher 6 and not by the fact that the valve 25 has become sealed. The inlet of the perpendicular pipe 34 being placed in the seal 28, the latter closes it and no longer allows the product 18, still flowing in the seat 27, to enter the perpendicular pipe 34. The pipe 33 is, as already described, closed by the gasket 28.

Cette conception est indispensable surtout dans les cas où le régulateur selon l'invention est utilisé pour pulvériser des produits 18, dont une quantité excessive à la sortie du gicleur 5, en séchant, pourrait l'obstruer.This design is essential especially in cases where the regulator according to the invention is used to spray products 18, an excessive amount of which at the outlet of the nozzle 5, while drying, could obstruct it.

La fig. 2 montre ladite deuxième forme d'exécution du régulateur selon l'invention en position de repos, le ressort 3 ayant poussé le piston différentiel 2 dans sa position de départ, tandis que la fig. 3 illustre la position du piston différentiel 2 durant l'utilisation, lorsque la valve 25, non représentée, est ouverte et le produit 18 s'écoule sous la pression la plus élevée qui peut régner dans le récipient, également non représenté.Fig. 2 shows said second embodiment of the regulator according to the invention in the rest position, the spring 3 having pushed the differential piston 2 into its starting position, while FIG. 3 illustrates the position of the differential piston 2 during use, when the valve 25, not shown, is open and the product 18 flows under the highest pressure which may prevail in the container, also not shown.

Dans cette deuxième variante préférée de l'objet de l'invention, la régulation se déroule ainsi qu'expliquée à l'aide de la fig. 4, de la façon suivante: dès l'ouverture de la valve 25 le produit 18 pénètre d'une part dans la chambre 17 du piston différentiel 2 et s'écoule d'autre part le long de ce dernier dans le canal d'évacuation 8a. Sous la pression du produit 18 le piston différentiel 2 est poussé en direction du gicleur 5 à l'envers de la force du ressort 3 qui est comprimé. La face frontale de la section de petit diamètre 12 du piston différentiel 2 est fermement pressée contre le centre d'un noyau 4 qui fait partie du gicleur 5 et est logé de son côté amont, de manière à ce qu'elle pénètre dans une chambre 23, dont elle diminue le volume. Des protubérences 22 du noyau 4 et un bord circulaire 19 du gicleur 5 sont en contact ferme avec la cage 1, de sorte que le produit 18 sous pression ne peut se déplacer vers le gicleur 5 qu'à travers de rainures-conduites 24 du noyau 4. Comme celles-ci sont perpendiculaires au canal d'évacuation 8a, on provoque à la sortie des rainures-conduites 24 des turbulences obstructrices. Du fait que les rainures-conduites 24 sont tangentielles par rapport à la chambre 23, le flux du produit 18, bien que turbulent, est soumis à un écoulement rotatif, perpétué par le bord circulaire 19 qui transforme le flux turbulent en flux laminaire qui alimente finalement le gicleur 5 par des canaux 21. Du fait que les turbulences sont transformées en flux laminaire, elles ne constituent plus qu'une force de freinage qui est d'autant plus forte que la pression du produit élevée, mais sans pouvoir atteindre une force de blocage du flux.In this second preferred variant of the subject of the invention, the regulation takes place as explained with the aid of FIG. 4, as follows: as soon as the valve 25 is opened, the product 18 penetrates on the one hand into the chamber 17 of the differential piston 2 and on the other hand flows along the latter into the evacuation channel 8a. Under the pressure of the product 18 the differential piston 2 is pushed in the direction of the nozzle 5 in reverse of the force of the spring 3 which is compressed. The front face of the small diameter section 12 of the differential piston 2 is firmly pressed against the center of a core 4 which is part of the nozzle 5 and is housed on its upstream side, so that it enters a chamber 23, the volume of which it decreases. Protrusions 22 of the core 4 and a circular edge 19 of the nozzle 5 are in firm contact with the cage 1, so that the product 18 under pressure can move towards the nozzle 5 only through grooves-conduits 24 of the core 4. As these are perpendicular to the discharge channel 8a, obstructive turbulence is caused at the outlet of the grooves-pipes 24. Because the grooves-conduits 24 are tangential with respect to the chamber 23, the flow of the product 18, although turbulent, is subjected to a rotary flow, perpetuated by the circular edge 19 which transforms the turbulent flow into laminar flow which feeds finally the nozzle 5 by channels 21. Because the turbulence is transformed into laminar flow, it no longer constitutes a braking force which is all the stronger as the pressure of the high product, but without being able to reach a force blocking the flow.

La freinage, imprimé au flux du produit 18 par les turbulences obstructrices est, dans cette exécution du régulateur, en fait une partie essentielle du début de la régulation du débit par unité de temps. En effet, le ressort 3 ne doit pas déplacer dès le début de l'évacuation du produit 18 le piston différentiel 2, mais seulement, lorsque la poussée du produit 18 diminue à un point où la section de passage pour le produit 18 doit être agrandie, afin qu'une quantité inchangée de produit 18 peut atteindre le gicleur 4 par unité de temps.The braking, imparted to the flow of the product 18 by the obstructive turbulence is, in this execution of the regulator, in fact an essential part of the beginning of the regulation of the flow rate per unit of time. Indeed, the spring 3 must not move from the start of the evacuation of the product 18 the differential piston 2, but only, when the thrust of the product 18 decreases to a point where the passage section for the product 18 must be enlarged , so that an unchanged amount of product 18 can reach the nozzle 4 per unit of time.

Les essais pratiques ont montré que normalement au moment de l'ouverture de la valve 25 le produit 18 sortant du gicleur 5 n'est pas encore pulvérisé, mais est expulsé sous forme de quelques gouttes de grande dimension. Ceci s'explique par le fait que le produit 18 n'est pas encore expulsé avec l'intégralité de la pression disponible, parce que la valve 25 ne s'ouvre pas instantanément.Practical tests have shown that normally when the valve 25 opens the product 18 leaving the nozzle 5 is not yet sprayed, but is expelled in the form of a few large drops. This is explained by the fact that the product 18 has not yet been expelled with all of the pressure available, because the valve 25 does not open instantly.

Pour éliminer ce phénomène, la tige 32 du poussoir 6 doit être munie d'un grand diamètre 32a, avec lequel elle s'appuie sur le joint 28, la conduite perpendiculaire 34 se trouvant immédiatement en dessous du diamètre 32a et n'ayant pas une section ronde, mais rectangulaire. De ce fait, lorsqu'on déplace le poussoir 6 vers le bas pour ouvrir la valve 25, elle reste plus longtemps obturée par le joint 28 qu'une conduite ronde qui, pour une section de dimension identique doit avoir un diamètre tel, qu'une partie de son entrée se trouve déjà dégagée du joint 28, avant que la valve 25 est suffisamment ouverte pour libérer toute la pression, sous laquelle se trouve le produit 18. Par contre, si la conduite perpendiculaire 34 est de section rectangulaire, elle exige d'une part un chemin de déplacement du poussoir 6 plus grand pour que son entrée soit dégagée du joint 28 et d'autre part, au lieu de présenter comme entrée une petite partie de sa section, elle présente quasiment instantanément, mais plus tard, la totalité de sa section d'entrée au produit 18 qui de ce fait se trouve expulsé avec toute la pression disponible, car la valve 25 est ouverte complètement, avant que la conduite perpendiculaire 34 est ouverte.To eliminate this phenomenon, the rod 32 of the pusher 6 must be provided with a large diameter 32a, with which it rests on the seal 28, the perpendicular pipe 34 being immediately below the diameter 32a and not having a round, but rectangular section. Therefore, when the pusher 6 is moved downward to open the valve 25, it remains closed for longer by the seal 28 than a round pipe which, for a section of identical size must have a diameter such that part of its inlet is already disengaged from the seal 28, before the valve 25 is sufficiently open to release all the pressure, under which the product 18 is found. On the other hand, if the perpendicular pipe 34 is of rectangular section, it requires on the one hand, a path for the displacement of the pusher 6 which is larger so that its entry is clear of the seal 28 and on the other hand, instead of presenting as a entry a small part of its section, it presents almost instantaneously, but later, all of its product entry section 18 which is therefore expelled with all the pressure available, because the valve 25 is fully open, before the perpendicular pipe 34 is opened.

Le régulateur selon l'invention tel que représenté en détail à la fig. 4 est constitué par la cage 1, le piston différentiel 2, le ressort 3 et le noyau 4 qui peut être fait d'une pièce avec le gicleur 5 et peut être logé soit dans le poussoir 6, soit dans un cylindre de montage 7, illustré par la fig. 6. Le canal d'évacuation est formé par des conduites 8, 9, 10 et 11. Afin de permettre au produit 18 de traverser les différentes conduites qui forment le canal d'évacuation 8a même si le piston différentiel 2 comprime le ressort 3 à bloc, le piston différentiel 2 est muni de rainures 16 et 16a. La force du ressort 3 est de préférence choisie de sorte que si le produit 18 est soumis à une pression initiale de 5 bar, le ressort soit comprimé à bloc pour permettre au piston différentiel 2 de s'appuyer fermement contre le noyau 4. Ce dernier est de préférence inséré dans le gicleur 5, de sorte qu'il forme avec le bord 19 de celui-ci un enfoncement 19a, duquel partent des canaux d'alimentation 21 du gicleur 5. La face amont du noyau 4 porte les protubérences 22 et sont centre présente la chambre 23, de laquelle partent les rainures-conduites 24, dont chacune forme tangente avec la circonférence de la chambre 23. La face amont des protubérences 22 et le bord circulaire 19 du gicleur 5 sont en contact ferme avec la cage 1, de sorte que les rainures-conduites 24 deviennent rééllement des conduites qui relient la chambre 23 à l'enfoncement 19a qui devient ainsi une conduite annulaire à partir de laquelle le produit 18 s'introduit dans les canaux d'alimentation 21 du gicleur 5.The regulator according to the invention as shown in detail in FIG. 4 is constituted by the cage 1, the differential piston 2, the spring 3 and the core 4 which can be made in one piece with the nozzle 5 and can be housed either in the pusher 6 or in a mounting cylinder 7, illustrated in fig. 6. The discharge channel is formed by pipes 8, 9, 10 and 11. In order to allow the product 18 to cross the various pipes which form the evacuation channel 8a even if the differential piston 2 compresses the spring 3 in block, the differential piston 2 is provided with grooves 16 and 16a. The force of the spring 3 is preferably chosen so that if the product 18 is subjected to an initial pressure of 5 bar, the spring is compressed in block to allow the differential piston 2 to press firmly against the core 4. The latter is preferably inserted into the nozzle 5, so that it forms with the edge 19 thereof a depression 19a, from which the supply channels 21 of the nozzle 5 start. The upstream face of the core 4 carries the protuberances 22 and are center presents the chamber 23, from which leave the grooves-conduits 24, each of which forms tangent with the circumference of the chamber 23. The upstream face of the protrusions 22 and the circular edge 19 of the nozzle 5 are in firm contact with the cage 1 , so that the grooves-conduits 24 become reellement of the conduits which connect the chamber 23 to the recess 19a which thus becomes an annular conduit from which the product 18 is introduced into the supply channels 21 of the nozzle 5.

La régulation du débit à l'aide du régulateur selon l'invention est illustrée par la fig. 7, dont la ligne 45 représente le débit de produit 18 par unité de temps, lorsqu'on utilise un gicleur du commerce, tandis que la ligne 36 montre le débit par unité de temps, obtenu lorsqu'on utilise un gicleur selon le brevet américain précité no 4,260,110 seul. La ligne 37 illustre le débit par unité de temps obtenu par l'utilisation du régulateur selon l'invention en commun avec le gicleur précité.The regulation of the flow using the regulator according to the invention is illustrated in FIG. 7, the line 45 of which represents the flow of product 18 per unit of time, when a commercial nozzle is used, while the line 36 shows the flow per unit of time, obtained when a nozzle is used according to the American patent No. 4,260,110 alone. Line 37 illustrates the flow rate per time unit obtained by using the regulator according to the invention in common with the aforementioned nozzle.

Claims (27)

1. Thrust regulator consisting of a differential piston (2) that is supported by a compression spring (3) which is lodged in a discharge channel (8a) for the product (18) that is inside of a container under gas pressure, and a differential piston (2), whose dimension are such with respect to those of the discharge channel (8a), that during the discharge of the product there exists at any time a minimum passage for the product (18), the differential piston (2) having extremities (12, 14) with different dimensions, whereby the larger surface (14) is directed towards the product flow (18), the spring (3) being tared so that under a predetermined pressure in the container it is compressed in order to put the differential piston (2) into a first end position that reduces the cross section of the discharge channel (8a) to a minimum opening, and the spring (3) is released proportionally to the decrease of pressure due to the ejection of product (18) from the container and displaces the piston (2) in order to obtain a progressive enlargement of the open cross section of the discharge channel (8a) until the piston (2) reaches a second end position, as soon as a predetermined minimum pressure has been attained in the container, whereby the shape of the piston (2) with respect to the shape of the discharge channel (8a) is such that with its displacement the piston guarantees that the product resulting from the multiplication of the pressure in the container by the remaining cross section can be maintained at least approximately constant, characterized in that the discharge channel (8a) leads into a chamber (23) from where channels (24) run off that form a tangent with the periphery of the chamber (23) and run into a circular channel (19a) from which feeding channels (21) of the spray nozzle (5) run off, the tangent channels (24) of the chamber (23) extending vertically to the discharge channel (8a) and the feeding channels (21) of th spray nozzle (5), whereby the front side of the low-pressure end (12) of the piston (2) firmly pushes against the high-pressure side of the nucleus (4) as a result of the highest pressure in the container, the cross sections between the piston (2) and the inner wall of the discharge channel (8a) are constantly being reduced in low-pressure direction, and there is a spring (3), whose strength is chosen in such a way that a predetermined pressure acting upon the surface of the product (18) compresses it such that the differential piston (2) is firmly pushed against the high-pressure side of the nucleus (4).
2. Regulator according to claim 1, characterized by the fact that the whole device is situated outside a container but inside a diffusion element (6, 7) of a valve (25).
3. Regulator according to claims 1 and 2, characterized by the fact that the whole device is situated in high-pressure direction and in the axis of the spray nozzle (5).
4. Regulator according to claim 1, provided with a thrustor, whose riser tube (32) is lodged in a valve (25) and contains a vertical duct (33), into which leads a horizontal duct (34), characterized by the fact that the thrustor (6) includes of a riser tube (32), which on one part of its exterior diameter (32a) has such a dimension and length that it is supported by the joint (28) of the valve (25), whereby the horizontal duct (34), which has a rectangular section, leads into a vertical duct (33) and the upper wall of the horizontal duct (34) being supported by the high-pressure end of the large exterior diameter (32a) of the riser tube (32).
5. Regulator according to claim 1, characterized by the fact that the largest section of the small diameter (12) of the piston (2) amounts to at least 94% of that of the smallest duct (8) of the discharge channel (8a).
6. Regulator according to claim 1, characterized by the fact that the largest section of the mean diameter (13) of the piston (2) amounts to at least 95% of that of the first intermediate duct (9) of the discharge channel (8a).
7. Regulator according to claim 1, characterized by the fact that the largest section of the large diameter (14) of the piston (2) amounts to at least 97% of that of the second intermediate duct (10) of the discharge channel (8a).
8. Regulator according to claim 1, characterized by the fact that the largest section of the large diameter (14) of the piston (2) amounts to at least 90% of that of the large duct (11) of the discharge channel (8a).
9. Regulator according to claim 1, characterized by the fact that the length of the large diameter (14) of the piston (2) is at least identical with that of the large duct (11) of the discharge channel (8a).
10. Regulator according to claim 1, characterized by the fact that the length of the large diameter (14) of the piston (2) surmounts the one of the large duct (11) by at least 25%.
11. Regulator according to claim 1, characterized by the fact that the volume of the piston (2), which is situated in the chamber (23) of the nucleus (4), at the maximum amounts to 16% of that of the chamber (23).
12. Regulator according to claim 1, characterized by the fact that the section of the circular channel (19a) amounts to 50% of the total of the sections of the tangent channels (24).
13. Regulator according to claim 1, characterized by the fact that between the low-pressure end of the mean diameter (12) of the piston (2) and the entrance of the duct (8) of the discharge channel (8a) there is a free space, when the piston (2) is pushed against the nucleus (4) of the spray nozzle (5), whereby the volume of the free space amounts to 0,05% of the one of the intermediate duct (9), minus the volume of the mean diameter (13) of the piston (2) that is situated in that duct (9).
14. Regulator according to claim 1, characterized by the fact that together with a spray nozzle (5) it is situated inside of a mounting cylinder, whose high-pressure end is provided with a bore, whose diameter is smaller than the large diameter (14) of the piston 2.
15. Regulator according to claim 1, characterized by the fact that the cage (1) disposes of three sections with different diameters, having respectively a large diameter (39) in high-pressure direction, a mean diameter (40) in the middle and a small diameter (50) in low-pressure direction, and the high-pressure end of the piston (2) having a larger diameter (14) than the one of the low-pressure end (12) whereby the distance (A) between the low-pressure end (12) of the piston (2) and the lower edge (61) of the feeding channel (60) of the spray nozzle (5) surmounts the small diameter (50) of the cage (1) by at least 150%, and the low-pressure end (12) of the piston (2) disposes of an aerodynamic shape to reduce the turbulence, and the length of the spring (3) corresponds at the minimum to the one of that part of the cage (1) with the mean diameter (40).
16. Regulator according to claim 15, characterized by the fact that the shoulder piece (15) of the differential piston (2), which supports the spring (3), serves as stopper to limit the course of the piston (3), when the latter is pushed in low-pressure direction because of the highest pressure that acts on the product (18).
17. Regulator according to claim 15, characterized by the fact that the length of the spring (3) is bigger than the one of that part of the cage (1) with the mean diameter (40).
18. Regulator according to claim 15, characterized by the fact that the high-pressure side of the piston (2) is provided with a chamber (171.
19. Regulator according to claim 15, characterized by the fact that the length of that section of the cage (1) with the largest diameter (39) is the same as the course the piston (2) covers under the highest pressure that acts on the product (18).
20. Regulator according to claim 15, characterized by the fact that the wall (41) of the channel (60), being situated opposite the entrance of the feeding channel of the spray nozzle (5), is bent.
21. Regulator according to claim 1, characterized by the fact that the spring (3) is a differential spring.
22. Regulator according to claim 1, characterized by the fact that the low-pressure side of the bearing surface (15) of the piston (2), which supports the spring (3), disposes of various grooves (16, 16a) that run parallel alongside (15) the piston's (2) axis and are surrounded with the spring (3).
23. Regulator according to claim 1, characterized by the fact that beside the spring (3) the whole device is made of cast plastics.
24. Regulator according to claim 1, characterized by the fact that the strongest spring (3) is compressed of a predetermined distance by a maximum pressure of 10.83 bar at an ambient temperature of 20 °C.
25. Regulator according to claim 1, characterized by the fact that the passage section between the low-pressure duct (8) and the small diameter (12) of the piston (3) amounts to 2,0 to 0,12 mm2 to regulate the flow of a product having a viscosity of more than 10 centipoise and to 0,12 to 0,06 mm2 to regulate the flow of a product having a viscosity below 10 centipoise, as the piston (2) is completely lodged in the low-pressure duct (8).
26. Regulator according to claim 1, characterized by the fact that the section of the large diameter (14) of the piston (2) is pushed by the force of the spring (3) in the direction of the valve (25), when the latter is closed.
27. Regulator according to claim 1, characterized by the fact that it is situated inside of a thrustor (6) of a valve (25), if the device is used with an aerosol can or bottle.
EP19830810512 1982-11-10 1983-11-08 Actuating regulator Expired EP0109361B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT83810512T ATE21675T1 (en) 1982-11-10 1983-11-08 THRUST REGULATOR.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH6534/82 1982-11-10
CH6534/82A CH650469A5 (en) 1982-11-10 1982-11-10 DEVICE FOR CONTROLLING THE THRUST OF A FLUID USING TURBULENCE.

Publications (2)

Publication Number Publication Date
EP0109361A1 EP0109361A1 (en) 1984-05-23
EP0109361B1 true EP0109361B1 (en) 1986-08-27

Family

ID=4311109

Family Applications (2)

Application Number Title Priority Date Filing Date
EP83903291A Pending EP0124542A1 (en) 1982-11-10 1983-11-08 Thrust regulator
EP19830810512 Expired EP0109361B1 (en) 1982-11-10 1983-11-08 Actuating regulator

Family Applications Before (1)

Application Number Title Priority Date Filing Date
EP83903291A Pending EP0124542A1 (en) 1982-11-10 1983-11-08 Thrust regulator

Country Status (22)

Country Link
US (1) US4650094A (en)
EP (2) EP0124542A1 (en)
JP (1) JPS59502061A (en)
AR (1) AR231955A1 (en)
AT (1) ATE21675T1 (en)
AU (1) AU568611B2 (en)
BR (1) BR8307603A (en)
CA (1) CA1260889A (en)
CH (1) CH650469A5 (en)
DD (1) DD212019A1 (en)
DE (1) DE3365713D1 (en)
DK (1) DK154414C (en)
ES (1) ES8503301A1 (en)
FI (1) FI74442C (en)
IE (1) IE54777B1 (en)
IL (1) IL70156A (en)
IN (1) IN159687B (en)
NO (1) NO160989C (en)
PT (1) PT77632B (en)
SU (1) SU1443794A3 (en)
WO (1) WO1984001930A1 (en)
ZA (1) ZA838356B (en)

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Also Published As

Publication number Publication date
DK154414C (en) 1989-05-08
EP0109361A1 (en) 1984-05-23
ES527136A0 (en) 1985-03-01
CH650469A5 (en) 1985-07-31
AU2128083A (en) 1984-06-04
IN159687B (en) 1987-05-30
PT77632A (en) 1983-12-01
DD212019A1 (en) 1984-08-01
IL70156A (en) 1990-04-29
NO842798L (en) 1984-07-09
AR231955A1 (en) 1985-04-30
SU1443794A3 (en) 1988-12-07
ATE21675T1 (en) 1986-09-15
ZA838356B (en) 1984-06-27
EP0124542A1 (en) 1984-11-14
FI842557A (en) 1984-06-26
IE54777B1 (en) 1990-01-31
IE832612L (en) 1984-05-10
PT77632B (en) 1986-03-12
FI74442B (en) 1987-10-30
BR8307603A (en) 1984-10-02
CA1260889A (en) 1989-09-26
FI74442C (en) 1988-02-08
NO160989C (en) 1989-06-21
ES8503301A1 (en) 1985-03-01
AU568611B2 (en) 1988-01-07
JPS59502061A (en) 1984-12-13
DE3365713D1 (en) 1986-10-02
DK154414B (en) 1988-11-14
DK336684D0 (en) 1984-07-09
NO160989B (en) 1989-03-13
DK336684A (en) 1984-07-09
WO1984001930A1 (en) 1984-05-24
JPH0749309B1 (en) 1995-05-31
FI842557A0 (en) 1984-06-26
IL70156A0 (en) 1984-02-29
US4650094A (en) 1987-03-17

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