PRESSURE MULTIPLYING AEROSOL PUMP

BACKGROUND OF THE INVENTION

Hand held spray dispensers are typically either of the manually-actuated spray pump type or the aerosol spray type. Aerosol spray dispensers utilize a liquefied gas propellant that “flashes off”, to create an ultra fine spray. These ultra fine sprays have mean droplet diameters on the order of about 40 microns. Such aerosol characteristic is desirable in many applications in cosmetics and industrial coatings. This sprayer however has several disadvantages. The composition contains large volume of liquefied gas and other volatile organic compounds (VOCs) which are known to react with certain nitrogenic oxides (NO_x), which in turn may result in the formation of ground-level ozone—a potential source of health problems. Certain propellants such as hydrocarbons and hydro-fluorocarbons gases also have a significant contribution to global warming. Therefore, there are ecological pressures to reduce, or avoid entirely, the use of VOCs in aerosol products.

Manually-actuated spray pump dispensers or finger pumps rely on the consumer to generate a hydraulic pressure in the pumping engine in order to dispense the fluid. Most pumping engines typically use a standard piston and cylinder arrangement in order to generate this hydraulic pressure. Thus, when the consumer applies an actuation force by pushing downward on the piston, the hydraulic pressure of the fluid in the cylinder is increased. Most manually-actuated spray pump dispensers have been unable to produce sprays having a mean droplet diameter of less than about 55 microns. These larger mean particle sizes, produced by conventional manual spray pumps is too coarse for many applications result in sprays that users refer to as “wet”.

Most conventional spray pumps operate at a hydraulic pressure of about 6 bar. Research has indicated that when the hydraulic pressure in these conventional spray pumps is increased upward to levels near about 14 bar, mean droplet diameters of about 40 microns or less are achievable.

A method of developing a high hydraulic pressure of about 14 bar requires actuation force to be applied from about 44 Newton to about 88 Newton. An actuation forces in this range is far too excessive for most ordinary consumers. Such an actuation force at this level can quickly fatigue the finger and hand of even the most physically adept person, let alone the typical users of most finger pumps.

Thus, a need exists for an aerosol method that is capable of delivering substantially higher hydraulic pressures and fine aerosol while reducing the ecological problems associated with existing propellant-based aerosols

The present invention provides a new dispensing device and method that effortlessly produces 14 bar of pressure for dispensing ultra fine spray. The device comprises of a spring-loaded piston member and valve system similar to that in a finger-triggered spray pump. The activation force however is generated by the expansion of liquefied gas stored in a small gas compartment within the pump. The piston is configured to multiply the gas pressure and transmit higher pressure to the fluid composition in the nozzle. It has been found that amount of liquefied gas that is need is about 1/10^thwhen compared to propellant-based aerosol that produces the same aerosol characteristics.

SUMMARY OF THE INVENTION

The present invention directed to hand-held dispensing device operable to dispense fluids or produce a spray of fine particles by hydraulic pressure. The device includes a cartridge containing a fluid to be dispensed and a pressure-multiplying piston pump actuated by liquefied gas pressure and manually controlled by a gas valve. The pump is configured to receive pressure from a compartment containing liquefied gas and transmit higher pressure to the fluid to be dispensed. The pressure multiplier produces high pressure, typically between 6-30 bar, which is suitable for generation of fine spray by hydraulic atomization. The device uses about 1/10^ththe amount of liquefied gas compared to a propellant-based aerosol therefore has substantial ecological benefits in relation to to air pollution and release of greenhouse gases.

The term propellant-based aerosol means a dispensing device that contains a volatile composition of liquefied gas and active fluid that is dispensed through a nozzle and rapidly dispersed as a fine aerosol. Such propellant-based aerosol described, for example in U.S. Pat. No. 3,207,386, U.S. Pat. No. 3,948,817, U.S. Pat. No. 4,254,104, U.S. Pat. No. 4,444,745, U.S. Pat. No. 4,536,323, and EP 0155697.

The dispensing device of the present invention will includes a cartridge containing fluid to be dispensed and a gas-actuated pressure-multiplying piston pump. The pump is connected to a source of pressure and controlled by a manually operated 3-way 2-position gas valve. The gas is stored in a separate compartment in a liquefied state. The piston is configured to amplify or multiply the gas pressure such that the pressure that is transmitted to the fluid is sufficient to produce aerosol of fine particles by hydraulic atomization.

It has been found that the quantity of liquefied gas that is required to dispense and aerosolized a volume of liquid to a given particle size using the embodiment of present invention is much smaller than the amount of liquefied gas needed to dispense and aerosolized the same fluid with commonly used propellant-based composition.

Commonly used propellants in cosmetic, household product and other aerosol coating products include volatile organic compounds (VOCs) such as propane, butane, 1,1-difluoroethane, and dimethylether. These VOCs are known to react with certain nitrogenic oxides (NO_x), which in turn may result in the formation of ground-level ozone—a potential source of health problems. Maximum incremental reactivity (MIR) is a measure of the ozone-forming potential of a compound and there are pressures to keep the calculated MIR value of products as low as possible. (For example: Regulation for Reducing the Ozone Formed for hairspray and Aerosol Coating—State of California). There are ecological pressures to reduce, or avoid entirely, the use of VOCs in cosmetic, household and in other industrial products.

The pressure-multiplier piston pump is comprised of a cylinder member and a spring-loaded piston member. The cylinder member includes a body with two unequal cylinder bores wherein with first cylinder bore has a larger diameter than the second cylinder bore. The spring-loaded piston member comprises of two integrally connected pistons wherein the diameter of the first piston is equal to the diameter of first cylinder bore and the diameter of the second piston is equal to the diameter of the second cylinder bore. The spring-loaded piston member is arranged to travel inside the cylindrical member.

The first large piston is in pressure communication relationship with gas pressure source via a control valve and the second piston is in fluid communication with the fluid to be dispensed. The first piston has a larger diameter than the second piston therefore, the pressure that is transmitted to the fluid increases in proportion to the areas of the pistons. High pressure is used to dispense fluid as an atomized spray or to dispense high viscosity fluids in the form a spray, a stream, a jet or the like.

Preferably, the pressure generated by the smaller piston is at least 10 bar, and more preferably 15 bar, and even more preferably 20, 25, 30 or 35 bar; yet the maximum pressure is typically be less than 50 bar.

The ratio between the area of the large piton and the small piton is typically greater than 1, 2, 3 or 4 but typically less than 10.

The term hydraulic atomization means that the fluid to be atomized is pressurized by the displacement of a piston and discharge to the atmosphere through an atomizing nozzle.

Effective nozzle that is commonly used in hydraulic atomization and can be used in the dispensing device the present invention is a pressure-swirl nozzle. Such nozzle induces a spinning motion to the fluid prior to exiting to the atmosphere. The spray that is discharged from a pressure-swirl nozzle breaks to fine fluid droplets. Higher pressure generally produces finer droplet. Alternatively, an aperture plate containing multiplicity of small apertures may also be used. Such aperture plate is commonly made by a process of nickel electroforming. Such aperture plate may contain a dense array of apertures, typically between 500-5000 apertures. The exit diameter of each aperture is typically between 6-20 micron and the thickness of the aperture plate is 75-100 microns.

The electroforming manufacture process produces apertures that have a flared or conical shape holes and a therefore low discharge coefficient.

The liquefied gas is selected from a group of hydrocarbon, hydro-fluorocarbon, unsaturated fluorocarbon or hydrofluoroolefin. Preferably the selected gas has low Global Warming Potential (GWP), less that 150, 130, 120 100, 50 and most preferably less than 6. Preferably, the liquefied gas will have low MIR value and is not considered a VOC by government agencies such as the United States Environmental Protection Agency (EPA). Preferably, the liquefied is not flammable.

Liquefied gases that have such properties are hydro-fluorocarbon such as Dymel™ HFA-152a, Ethane, DME (dirnathyl ether) and particularly HFO-1234ze. In some cases a blend of hydrocarbon, unsaturated fluorocarbon or hydro-fluorocarbon may also be used. For example, 88% HFO-1234ze and 12% Ethane may be used to alter the vapor pressure and the degree of flammability. The above mentioned composition has a vapor pressure of 108 psi. Alternative blend of 50% HFO-1234ze and 50% HFC-152a may also be used. Such blend has lower flammability than HFC-152a. The concentration of HFO-1234ze may be 100, 88, 80, 70, 60, 50 40 30 20 percent and the balance maybe any hydrocarbon gas including ethane, or hydro-fluorocarbon specifically HFA-152a.

Various blends that can be used in the dispensing device of the present invention are disclosed in the publication titled “Propellant and Solvent 2012 and Beyond Strategies tier the 21^st”, Century Published by Southern Aerosol Inc. and in “An Introduction to Aerosol Propellant” published by Diversified CPC International, Inc.” Both documents are incorporated here by reference.

The dispensing system further includes a control valve which controls the supply of gas pressure or atmospheric pressure to the pump. The valve can switch between the gas pressure port and the atmospheric pressure port. At the normal position the pump is connected to the atmospheric pressure port and the spring-loaded piston is biased by it spring to one end of the cylinder. In the second position valve is connected to the gas pressure port and the piston is displaced to the opposite end of the cylinder while compressing the spring and dispensing fluid. When the control valve is switched back to atmospheric pressure the gas is released to the atmosphere and the piston returns by its spring to the normal position while drawing more fluid from the container.

The control valve switches between the gas pressure port and atmospheric pressure port by a finger actuation or the like.

BRIEF DESCRIPTION OF THE DRAWINGS

Having thus summarized the general nature of the invention and some of its features and advantages, certain preferred embodiments and modifications thereof will become apparent to those skilled in the art from the detailed description herein having reference to the figures that follow, of which:

FIG. 1 is a simplified schematic view of the pressure multiplying dispensing system illustrating the main building blocks in accordance with of the present invention.

FIG. 2 is a simplified cross sectional view of pressure-multiplying dispensing system in accordance with certain embodiments of the invention.

FIG. 2A is simplified enlarged cross sectional view of the pressure multiplying dispensing system shown in FIG. 2.

FIG. 3 is a simplified exploded view of certain pressure-multiplying dispensing system which include fluid container.

FIG. 3A is a cross sectional view of the pressure multiplying dispensing system showing the position of the piston, the valves and the direction of fluid flow when the control valve is pressed

FIG. 3B is a cross sectional view of the pressure multiplying dispensing system showing the position of the piston, the valves and the direction of fluid flow when the actuation valve is released.

FIG. 3C is a detail view of rocker arm actuator.

FIG. 3D is a side view in a perpendicular direction relative to the view shown in FIG. 3B.

FIG. 6 is a simplified cross sectional view of pressure-multiplying dispensing system in accordance with certain embodiments of the invention.

FIG. 6A illustrates enlarged cross sectional views of pressure swirl nozzle shown as Detail B of FIG. 6.

FIG. 6B illustrates enlarged cross sectional views FIG. 6A without the press swirl nozzle.

FIG. 6C is a detail view of certain pressure-multiplying piston.

FIG. 6D illustrates an exploded view that best shows the interconnection between external components in accordance with certain embodiments of the invention.

FIG. 6E illustrates a perspective view that best shows the interconnection between external components system in accordance with certain embodiments of the invention.

FIG. 6F is a simplified illustration showing of an attachment method of cylinder body and top cover system in accordance with certain embodiments of the invention.

FIG. 7 is a detail view which illustrates nozzle insert in a side view.

FIG. 7A is a detail view illustrate nozzle insert in a thntal view.

FIG. 8 is a graphic illustration showing the relation between the diameter of the swirl chamber, the droplet size and the cross sectional vane exit in accordance with certain embodiments of the invention.

FIG. 9 is a graphic illustration showing the relation between pressure and the droplet size in accordance with certain embodiments of the invention.

DETAIL DESCRIPTION OF THE INVENTION

FIG. 1 illustrates a schematic diagram in accordance to an exemplary embodiment of dispensing system (100). Dispensing system (100) includes a pressure-multiplying pump (110) operable by a liquefied gas pressure (120) and manually controlled by valve (140). Dispensing system (100) is configured to draws fluid (131) from a container (130) and dispensed it through nozzle (115) as an atomized spray (116) at a pressure that is greater than gas pressure P.

Pressure-multiplying pump (110) includes a cylinder body (111) and a spring-loaded piston member (112). When pressure P is applied to cylinder (111A), spring-loaded piston (112) is displaced from the proximal to the distal end of cylinder (111) while spring (117) is compressed. When the pressure in cylinder (112A) is exhausted to the atmosphere spring-loaded piston (112) returns by the force of its spring (117) back to the proximal end of cylinder (111). The movement of the piston from the distal to the proximal end draws fluid from the container into cylinder (111B) while the movement in the reverse direction dispenses fluid through nozzle (115). A pair of check valves (113) and (114) restricts the movement of fluid (131) from the container (130) to nozzle (115).

Pressure multiplying pump (110) is arranged to amplify the gas pressure and transmit higher pressure to fluid (131). Cylinder (111) comprising of a stepped bore having a large diameter portion (111A) and a small diameter portion (111B). Accordingly spring-loaded piston member (112) includes a pair of axially-connected pistons (112A) and (112B) that diametrically matching cylinders (111A) and (111B) respectively. In this way the gas pressure P that is applied to cylinder (111A) produces higher fluid pressure in cylinder (111B). The fluid pressure equals to the arithmetic product of the gas pressure P and the ratio between the areas of pistons (112A) and (112B). High pressure may be used to effectively atomizes fluid or dispense a flowable viscous fluid. Fluids with high viscosity up to 50000 cP or even 100000 cP may be dispensed.

The pressure multiplier of the present invention is configured to increase the gas pressure and transmit higher pressure to the fluid composition at the nozzle. The actual pressure is also dependent on pressure loss at the nozzle (115). Preferably, nozzles with low discharge coefficient will be used, such as those describe in U.S. Patent Publication 2006/0275220 and U.S. Pat. No. 5,711,488.

Cylinder (111) includes a venting port (118) near the junction between cylinder (111A) and (111B) to prevent compression of the air between piston (112A) and (112B).

Valve (140) controls the operation of dispensing unit (100) by switching the connection of pump inlet port (142) to either gas pressure port (143) or to exhaust port (141). At the normal rest position pump inlet port (142) is connected to the exhaust port (141) and piston (112) is biased by the spring (117) to the proximal end of the cylinder (111). At the “on” position pump inlet port (142) is connected to gas pressure port (143) and the piston is displaced to the distal end of the cylinder while spring (117) is compressed. When control valve (140) is switched back to normal rest position, piston (112) returns by spring (116) to the proximal position. The reciprocating movement of piston (112) moves fluid from container (130) and dispense it through nozzle (115) at a pressure that is greater than the gas pressure.

In one embodiment the diameter of piston (112A) is 12 mm and the diameter of piston (112B) is 6 mm, therefore, the area of the first piston (112A) is 113 mm²and the area of piston (112B) is 28.2 mm². The ratio between the areas of the two pistons is about 4, therefore the pressure that is applied to the fluid by piston (112B) is approximately 4 times higher than the gas pressure. Due to friction force between the piston and the cylinder, the opposing spring force and pressure loss at the nozzle the actual pressure may be lower, typically up to 20% lower.

Spring (118) is configured to move piston (112) from the distal to the proximal end of the travel such that fluid is drawn from the container (130) to the cylinder (111B) conveniently fast such that the user does not have to wait more than a fraction of a second between actuation, preferably not longer than 100-400 msec.

In one embodiment the liquefied gas stored in gas compartment (120) is DYMEL™ HFC-152A manufacture by DuPont Company Wilmington, Del. (CAS Number 75-37-6). DYMEL™ HFC-152a has a vapor pressure of 4.16 bar at 20 Deg C. Therefore the pressure that is transmitted to the fluid is 16.6 bar, 4 time higher than the gas pressure. Such pressure effectively produces fine droplets with droplets size of 40 micron. The amount of DYMEL™ HFC-152a that is needed to atomize 1 cubic-centimeter of fluid at 16.6 bar is only 0.0451 gram; therefore the ratio between the weight of the gas and the liquid is 1/0.0451 or 4.51% by weight. In comparison, the percentage weight of the liquefied gas in a conventional propellant-based aerosol is about 20%-35% by the total weight of the composition (Ref: Cosmetic and Toiletry Formulation by Ernest Flick).

The dispensing method of the present invention substantially reduces the amount of liquefied gases that are required to aerosolize a liquid and therefore has ecological and health benefits.

Fluid container (130) may contain at least 35, 65 or 95, 250, 500, 1000 ml fluid but typically less than 2000 ml. Preferably the container is made of plastic material such as polypropylene, PET or PE.

Dispensing system (100) may be used to dispense aerosols of cosmetic compositions such as deodorant or hairspray. U.S. patent publication 2006/0275220 has shown models of liquid cosmetic compositions which may be atomized by high hydraulic pressure. Such cosmetic compositions are shown in Table-1 of the above patent publication. Table-2 of the above publication shows the droplets size (Dv, 0.5) as a function of nozzle pressure for the compositions in Table 1.

In can be seen that excellent spray quality attainable by use of high pressure with the appropriate nozzle system. Patent publication 2006/0275220 entitled “A Method of Creating Cosmetic Spray”, is hereby incorporated by reference.

FIG. 2 illustrates an exemplary embodiment of dispensing unit (200) which includes a fluid container (130), a threaded locknut (135) which includes a gasket (133) for hermetically sealing dispensing unit (200) to container (130) and a dip-tube (132) for drawing the liquid from the container. Preferably the container will include a standard S.P.I neck finish thread with a nominal diameter of 13 to 75 mm and with type 400, 410 or 415 continuous threads. The container is made of plastic material that is commonly used for packaging fluid. Standard materials will include high-density-polyethylene (HDPE), post consumer resin (PCR), low-density-polyethylene (LDPE), polypropylene (PP), K-Resin Polyvinyl Chloride (PVC), PETG or PET.

FIG. 2A illustrates a cross sectional view of dispensing unit (200A) which includes a pressure multiplying pump (110), a gas compartment (120), and a control valve (140) (bounded by dashed line).

Pressure multiplying pump (110) comprising a stepped cylinder bore (111) and reciprocating piston member (112) which includes a pair of axially-connected pistons (112A) and (112B). The pistons are arranged to slide along the axis of the cylinders (111A) and (111B) while maintaining a hermetically tight sealing interference. This arrangement is configured to multiply the gas pressure as described earlier in relation to dispensing unit (100).

In one preferred embodiment the diameter of piston (112A) is 12 mm and the diameter of piston (112B) is 6 mm. Thus, the area of the first piston (112A) is 113 mm²and the area of piston (112B) is 28.2 mm². The ratio between the area of two pistons is about 4, hence the nominal pressure that is applied to the fluid by piston (112B) is 4 times higher than the gas pressure. The liquefied gas stored in chamber (120) is Dymel™ HFC-152A which has a vapor pressure of 4.3 bar at 20° C. Therefore the pressure that is applied to the fluid by piston (112B) is about 17.3 bar. Such pressure is suitable for dispensing viscous material or to dispense spray of very fine particles, typically smaller than 40 micron.

The actual pressure may be about 10% to 15% lower than the calculated pressure due to friction between the piston and the cylinder wall, the force of the spring (117) and the pressure loss at dispensing nozzle (115).

The displacement of piston (112) is about 10, 20, 30, 40, or 50 mm but typically less than 100 mm. Thus, the corresponding dispensing volume may be 0.282, 0.564, 0.846, 1.128 or 1.41 ml but typically less than 4 ml or 6 ml. Higher volume requires less actuations therefore allowing more convenient operation which may be preferred for certain applications such as air freshener, hairspray, body deodorant or the like.

Dispensing unit (200A) further includes a gas compartment (120) which contains liquefied gas. Gas compartment (120) defines an annular cavity in a concentric relationship to the cylinder bore (111). The annular cavity defines a partial circular cutout around the cylinder bore (111). The gas cavity (120) revolves about 175 degrees in the clockwise and counterclockwise directions relative to the sectional view shown in FIG. 2A. This partial annular cavity leaves about 10 degrees of angular space for the valve (113) and nozzle (115). Preferably the gas cavity is geometrically configured to form a uniform wall thickness within housing (110) and the cylinder cavity (111). Even wall thickness is preferable in plastic molding processes.

Liquefied gas is stored in the annular compartment (120) within a porous polyethylene member (121). Porous member holds the liquefied gas in place regardless of the orientation of dispensing unit (200A). Suitable porous member will have about 40, 50, 60 or 70 percent porosity relative to the total volume of the member. The total volume of the liquefied gas is calculated using the ideal gas law based on pressure multiplication and the total volume of liquid to be dispensed.

Pistons (112) are loaded by a spring (117) which is configured to displace piston (112) from to the distal to the proximal end of the piston travel. Spring (117) has sufficient force to displace the piston from the distal end to the proximal end within 100, 200, 300 msec. Excessive spring force reduces the pressure that is transmitted to the fluid. Similar spring-loaded pistons are commonly used in finger-trigger pumps such as Calmar model HF-20325 or HF-16398 or HF-20826 or Seaquist model HF-18551 or HF-21223 or HF-19766 all are distributed by McKernan Packaging, Reno, Nev. USA. In one embodiment the first 3 or 4 spring coils (117A) has a reduced external diameter which serves to keep ball (113) within the valve (113A), preferably at 1-3 mm away from valve seat.

The description of the spring (117) and other component that are commonly used in finger-trigger piston pump are not intended to be exhaustive since they are very well known by those skilled in the art. This also includes, check valve (113), piston skirt sealing methods, material selection and the like. Modifications or variations of these components are possible and contemplated in light of the above teachings.

Check valve (113) includes a floating ball having a diameter of 3 mm configured to seal a 60 deg. valve seat. The ball is restricted to float between the valve seat and the seat of spring (117). This arrangement is normally employed in finger-triggered pumps such as those described above.

Valve (140) comprising a cylindrical cavity (149) which includes two orifices, the first orifice (143A) is connected to gas pressure port (143) and the second orifice (141A) is connected to the exhaust port (141). Cylindrical cavity (149) further includes a passageway (142) which extends from the cavity to the cylinder (111A). The valve further includes a plunger (146) that is configured to move axially between the two orifices within the cavity (149) such that end-faces (148A) or (148B) of plunger (146) selectively seals, either the first, or the second orifice.

Plunger (146) is made of cylindrical neodymium magnet which is polarized in the axial directions. Cavity (149) further includes a ferromagnetic iron washer (147) seated at the end of the cavity and configured to magnetically pull plunger (146) toward the gas pressure orifice (143A). In this way end face (148B) shuts the gas pressure orifice (143A). Valve (140) further includes a moveable magnetic disk (145) operable to defeat the magnetic attraction between plunger (146) the ferromagnetic disk (147). When magnetic disk (145) is moved to a close proximity from the magnetic plunger (146) the plunger is then pulled away to the opposite end of the cavity thereby closing the exhaust orifice (141A) and opening the pressure orifice (143A), consequently, gas flows from (143A) through passageway (142) to cylinder (111A) and displaces piston (112) to the distal end of cylinder (111) as described earlier in relation to the preferred embodiment (100).

In one embodiment plunger has a cylindrical body with an outside diameter of 5 mm and an inside diameter of 1.5 mm. An elastomeric member (148) facilitates hermetic closure of the orifices. Elastomeric member (148) is made of FKM, EPDM or silicon rubber.

Magnetic disk (145) is seated on a spring-loaded knob (151) which is activated by pressing a finger (152) to move the knob closer to plunger (146). Spring (150) is configured to return knob (151) back to a normal position when the finger pressure (152) is released.

The magnetic attraction force between plunger (104) and the ferromagnetic insert provides about 0.40-0.60 Newton. The diameter of the gas port is typically between 0.5 to 1 mm.

Dispensing unit 200A may be used for dispensing air freshener liquids when it desirable to achieve a Sauter D[4,3] mean droplet size of from 20 μm to 60 μm, or in particular from 20 μm to 50 μm, and especially from 25 μm to 35 μm. The desirable pressure at the nozzle should be from 8 to 30 bar and preferably from 15 to 25 bar but typically less than 40 or 30 bar. The pressure may be configured by properly selecting the pressure amplification of the pistons and the liquefied gas.

The spray system may be used for dispensing cosmetic compositions include hair sprays, body sprays, deodorants, antiperspirants, and perfumes. Body sprays and hair are particularly suitable as they require small droplet size,

High flow rates, for example from 0.1 g/s to 1.0 g/s, and, in particular, from 0.2/s to 0.6 g/s, can be achieved, while still maintaining good spray quality. Spray quality may be defined by the size of the droplets and droplet size distribution of said droplets. For many applications, it desirable to achieve a Sauter D[4,3] mean droplet size of from 7 μm. to 60 μm, in particular from 10 μm to 50 μm, and especially from 15 μm to 35 μm. It is further preferred that for each of the Sauter D[4,3] preferred ranges indicated above, that the Sauter D[3,2] mean droplet size is also within the same range. The median volume droplet size (Sauter D[v,0.5]) and it is preferred that this value is from 7 μm to 60 μm, in particular from 10 μm to 50 μm, and especially from 15 μm to 35 μm. With regard to the narrowness of the droplet size distribution, it is preferred that the gap between the Sauter D[v,0,1] value and the Sauter D[v,0.9] value is 50 microns or less, more preferably 45 microns or less, and especially 40 microns or less.

Handheld aerosol/spray system according to the present invention may have a product volume of at least 30, 60 or 90 ml, but less than 1000, 800 or 600.

FIG. 3 illustrates an exploded view of an exemplary embodiment of dispensing unit (300) which includes a pressure multiplying pump (110), a fluid container (130), a dip-tube (132) and a locknut (200) for connecting the pump (110) to container (130).

In one embodiment container (130) includes a bottom face that moves up toward the pump (110) due to vacuum resulting from the discharge of the container content. Such configuration described in U.S. Pat. No. 8,499,970, the entirety of which is hereby incorporated by reference.

FIG. 3A illustrates a cross sectional view of dispensing unit (300) having a housing (160) which includes a pressure multiplying pump (110) and a gas compartment (120). The dispensing unit further includes a control valve (140) that is attached to housing. Housing (160) and the valve unit (140) include a first passageway (143) connecting gas compartment (120) to the valve unit (140) and a second passageway (119) connecting fluid container to the nozzle (115).

Pressure multiplying pump (110) comprising a stepped cylinder bore (111) and reciprocating piston member (112) which includes a pair of axially-connected pistons (112A) and (112B). The pistons are arranged to slide along the axis of the cylinders (111A) and (111B) while maintaining a hermetically tight sealing interference under pressure. This arrangement is configured to multiply the gas pressure as described earlier in relation to dispensing unit (100).

The diameter of first piston (112A) is 34.92 mm and the diameter of the second piston (112B) is 17.46 mm. Piston (112A) is in pressure communication relationship with a source of gas pressure through the valve (140) and piston (112B) is fluid communication with the liquid to be dispensed. The ratio of the area of the piston (112A) and (112B) is 4. In this way the pressure that be transmitted to the fluid may be 4 time greater than the gas pressure applied to piston (112A).

Each piston is provided with a flexible skirt-like lip seal that is oriented to expand against the cylinder wall under pressure.

The displacement of piston (111) is 4 mm such that the volume of the liquid that is displaced upon each stroke of the piston is an arithmetic product of the area of the small piston (112B) and its travel. The embodiment described herein displaces a volume of 0.619 mL.

The displacement and the diameter of the piston may be configure to displace larger or smaller volume, typically in personal care or household application the volume is 0.2, 0.3, 0.4, 0.5, 0.7, 0.8, 1, 2 mL but generally less than 4 mL. The diameter of the larger piston (112A) is less than 50 mm but greater than 10 mm, 20 mm, 30 mm, or 40 mm. High volume reduces the number of actuations which may be preferred in some application or by some users, for example, when applying hairsprays or deodorants in a continuous manner.

The ratio between the diameters of piston (112A) and piston (112B) may be selected according to the consumer preference or the application. Typically the ratio is greater than 1, 2, 3, 4, or 5 but generally smaller than 10.

The pump includes a gas compartment (120) which contains 5 gm of liquefied gas Dymel™ HFC-152A to dispense 100 mL at about 20 bar of pressure. Gas compartment (120) may contain 6, 7, 8, 9, 10 gram of liquefied gas to dispense higher volume proportionally. A blend of two or more liquefied gases may also be used, such as a blend of HFO-1234ze and Ethane or HFO-1234ze and Dymel™ HFC-152a. Gas compartment (120) contains gas under the vapor pressure. Gas compartment (120) will have a sufficient strength to safely withstand the vapor pressure of the selected gas at 50° C. The structural stress of gas compartment may be analyzed and optimized using the Finite Element Analysis computation code available from Ansys Inc., Canonsburg, Pa. USA. Plastic material such as PET may be selected to minimize permeation of the gas through the wall. The wall thickness of gas compartment (120) is about from 1.0 to 2.5 mm. Structural ribs may be provided to enhance the strength of gas compartment (120). Preferably the wall thickness of housing (160) is as uniform as possible.

Control valve (140) is configured to connect gas pressure from compartment (120) to the cylinder (111A) or to discharge gas pressure from the cylinder (111A) to the atmosphere. Control valve comprises a hermetically sealed enclosure (149) which includes a gas inlet orifice (143A), a gas exhaust orifice (141A) and a passageway (142) to cylinder (111A). Control valve (140) includes a rocker arm (145) that selectively opens inlet orifice (143A) and close exhaust orifice (141A) or oppositely, close inlet orifice (143A) and open exhaust orifice (141A). The rocker arm (145) makes small rotational movement about a pivot (151) to open one orifice and close the second orifice. The rocker arm is shown separately in FIG. 3C. It can be seen that rocker arm (145) includes two sealing members (148), (147), a pivot hole (151), a push knob (152), and an o-ring (146).

The sealing members (147), (148) are made from soft elastomeric material such as Silicon rubber, FKM or EPDM which have a hardness value of 60, 70, 80 or 90 Shore Durometer A. The sealing member may be over-molded as an integral part of the rocker arm (145).

FIG. 3B illustrates dispensing unit (300) when valve (140) is in a closed or normal position. Rocker arm is normally biased by a spring (150) to rotate in the clockwise direction. In this way gas inlet orifice (143A) is closed and exhaust orifice (141A) is open to the atmosphere. In the normal position cylinder (111A) is vented to the atmosphere and piston (112) is force by a spring (117) to the proximal end of the piston travel. Referring back to FIG. 7B it can be seen that when control valve (140) is press by a finger (112) (or the like) rocker arm (145) rotates in the counterclockwise direction to close the exhaust orifice (141A) and open the pressure orifice (143A). In this position gas flows to the cylinder through passageway (142) and piston (112) moves from the proximal to the distal end of the travel. This movement displaces the fluid through the dispensing nozzle (115) as indicated by the arrow marked “Fluid Flow”. It can be seen that check valve (113) closes and check valve (114) opens thereby restricting the flow of fluid to the dispensing nozzle.

Gas compartment contains liquefied gas HFC-152a which maintains a constant pressure of about 5 bar at 21° C. The pressure that is transmitted to the fluid is multiplied by the ratio of the areas of the pistons (112A) and (112B), which is approximately 4. The pressure that is applied to the fluid is therefore about 20 bar, 4 times higher than the gas pressure. The pressure is measured when the flow through (115) nozzle is fully restricted. When the nozzle is open the dynamic pressure may be up 30 percent lower. Actual pressure is also depended on fluid viscosity and the force of spring (117). These parameters and the ratio between the areas of pistons (112A) and (112B) may be configured to achieve the desirable pressure and spray characteristics in accordance to the present invention.

Spring (150) will produce force that is sufficient to shut the opening of the gas nozzle (143A) at elevated temperature of 60° C. when the gas vapor pressure is about 12 bar. The diameter of orifice (143A) is 0.5, 0.7, or 1 mm. Sealing member is configured to apply less than 2 Newton to seal nozzle (143A). Preferably the spring force will apply about 20%, 30% or 40% higher force to safely shut the gas orifice.

Dispensing unit (300) further includes a pneumatic means to equalize the pressure in the container as the fluid being dispensed. FIG. 3D illustrates a cross sectional view of the dispensing unit (300) which is perpendicular to the views in FIG. 3A.

Dispensing unit (300) uses the exhaust gas flow that is discharged from the cylinder (111A) to opens a venting channel to the container. Dispensing (300) include a venting channel (160) which includes one opening (160A) to the atmosphere and a second opening to the fluid container (160B). Dispensing unit further includes a spring-loaded plunger (170) which normally blocks venting channel (160). Plunger (170) slides in channel (161) which intersects perpendicularly with venting channel (160). Spring-loaded plunger (170) is normally positioned at the intersection between channel (160) and channel (161) to seal the passage of venting channel (160) to the atmosphere. When the gas is discharges through nozzle (141) plunger (170) is displaced from the intersection thereby opening the venting channel (160) to the atmosphere.

FIG. 6 illustrates a cross sectional view of an exemplary embodiment of dispensing unit (600) which includes a pressure multiplying pump (110) and a gas cartridge (120) which includes control valve (140).

Pressure multiplying pump (110) comprised of a cylindrical member (111) with two unequal cylinder bores (111A) and (111B). The first cylinder bore (111A) has a larger diameter than the second cylinder bore (111B). Pump (110) further includes a piston member (112) comprising of two integrally connected pistons (112A) and (112B). The diameter of the first piston (112A) is equal to the diameter of the first cylinder bore (111A) and the diameter of the second piston (112B) is equal to diameter of the second cylinder bore (111B). This arrangement is configured to multiply the gas pressure as described earlier in relation to dispensing unit (100).

FIG. 6C shows an alternative piston member (112) which has uniform wall thickness of about 1 mm and a skirt-like sealing arrangement for each piston (112AS) and (112BS) configured to seal the piston against the cylinder bore under pressure. Such seal is commonly used in a finger-triggered spray pump disclosed for example in U.S. Pat. Nos. 6,050,457, 6,050,457, 4,775,079, 5,353,969 all of which are incorporated here by reference. The area of piston member (112A) is indicated by the letter A and the area of piston member (112B) is indicated by the letter B.

Dispensing unit (600) includes a miniature canister (120) containing liquefied dimethylether (125) which provides a source of pressure to operate the pump. Canister (120) includes a stem valve (140) which controls the release of pressure from the canister to the cylinder (111A).

Stem valve (140) is attached to the opening of the canister (120) by a crimping or by any other process recommended by the manufacturer of such valves. Stem valve that may be used include Lindal Model CA39 F manufactured by Lindal Group Hamburg Germany, or Summit Model SV-77 manufactured by Summit Packaging System Manchester, NH USA. Stem valve (140) includes a tube (143) that extends from the inlet opening of stem valve (140) to the gaseous space of the canister. Tube (143) extends to about 1 mm from the base end (120B) of the canister (120). The canister may contain less than 90, 80 or 70 percent gas in liquid state and the balance in gaseous state. The canister is made of metal such as aluminum or plastics, preferably clear plastic such as PET. The wall thickness of the canister is dimensioned to withstand the vapor pressure of the gas at 60° C. The wall thickness may be calculated using the finite element method. Typically, the wall thickness of the canister is about 0.3, 0.4, 0.5, 0.6 0.7, 0.8, 0.9 mm but less than 3 mm. Due to rapid discharge of gas from the canister to cylinder bore (111A) there will be a slight temperature decrease in the liquefied gas. Temperature decrease reduces the gas pressure. In order to minimize temperature decrease canister (140) may contain a mixture of liquefied gas and water such that the heat capacity of the water will prevent rapid temperature decrease. Typically, the canister contains less than 20, grams of liquefied gas of which the amount of water is 50% or less (by weight of the total composition). However, it should be understood that the volume of the canister and the amount of gas that is contained in the canister is a function of the pressure multiplication and the total amount of the fluid to be dispensed. The total amount of liquefied gas is not limited in the present invention.

Dispensing unit (600) further includes a top cover member (150) which is configured to seal the opening of cylinder (111A). Member (150) includes a circular protrusion (152) that plugs the opening of cylinder (111A) in a pressure-tight sealing engagement. Top cover (150) further includes a socket (151) for securely housing canister (140). Socket (151) is dimensionally configured to allow a sliding interference of canister (120) along the axis of the socket (151). A pair retaining tabs (not shown in this view) keeps the canister in place within socket (151) in any possible orientation of dispensing unit (600).

Cylinder cover further includes a gas inlet nipple (142) through which the stem valve pressurizes cylinder (111A). Nipple (142) includes an elastomeric washer that seals between the interface between the stem valve and nipple (142). At the normal resting state stem valve (140) is in loose contact engagement with gas inlet nipple (142). Loose contact allows atmospheric pressure communication to cylinder (111A). When the user presses on the canister base (120B), as shown by the illustration of finger (112), stem valve (140) engages with the nipple (142) to seal the inlet of the stem valve (140), subsequently the valve opens and gas pressure is released to cylinder bore (111A). Piston member (112) moves to the distal end of the travel while fluid is displaced through check valve (114) and discharged from dispensing nozzle (115).

Check valve (114) includes a spherical acrylic ball and a 60 degrees valve seat. The ball is normally biased by a spring against the valve seat such that the valve opens when the fluid pressure is greater than 0.3, 0.4, or 0.6 bar but typically less than 1 bar.

When the finger pressure (112) is released stem valve (140) closes, consequently compression spring (117) displaces piston member (112) back to the proximal end of the travel. Fluid is drawn from the container (not shown) through dip tube (132) and check valve (113) into the cylinder bore (111B). Simultaneously, gas pressure from cylinder (111A) is discharged through the nipple (142) and passage (154) to the atmosphere.

Spring (117) will have the sufficient force to return piston (112) from the distal end of the travel to proximal end of the travel within 100, 200 300 msec. The spring may be configured with accordance to fluid viscosity. Typical compression spring (117) will have a wire diameter 0.2-1 mm and external diameter from about 3 to 10 mm and typically less than 30 coils.

FIG. 6C illustrates piston member (112) separately for the purpose of clarity. The diameter of piston (112A) is 13 mm and the diameter of piston (112B) is 8 mm. Thus the area (A) of piston (112A) is equal to 132.7 mm²and area (B) of piston (112B) is equal to 50.2 mm². The total amount of liquefied gas that is required to dispense a volume of liquid may be calculated according to the ideal gas law.

Conveniently, the pressure multiplication factor is defined by the letter k according to the following equation:

$k := \frac{A}{B}$

Substituting the values of the piston areas A and B:

- k=2.641

The pressure that is transmitted to the liquid equals the arithmetic product of the vapor pressure (5 bar) and pressure multiplication factor k.

P(liquid)=5*K=13.2 bar

The mass of liquefied dimethyl ether (DME) that is needed to dispense 1 mL of fluid at 13.2 bar is calculated according to the Ideal Gas Law

$n := \frac{Pvap \cdot V \cdot k}{R \cdot T}$

n=number of moles of dimethyl ether (DME))

Pvap=5 bar (vapor pressure of DME)

R−=8.314 J joule/K mole (gas constant)

T=293 K (temperature in Kelvin)

V*k is the volumetric displacement of piston 111A to dispense 1 ml of fluid

$n = 5.247 \times 10^{- 4} mol$

$M := 46.7 \frac{gm}{mol}$

M=molecular weight of dimethyl ether

weight:=M·n

weight=0.025·gm

The total weight of dimethyl ether that is required to dispense 1 mL of fluid at 13.2 bar is 0.025 gram or 2.5 percent when calculated as a percentage of total weight of liquid (assuming that the liquid density is 1 gm/ml). In comparison, the amount of dimethyl ether in propellant-based aerosol is 30, 40 or 50 percent.

FIG. 6A and FIG. 6B illustrate enlarged cross sectional views of atomizing nozzle shown as Detail-B in FIG. 6. For clarity FIG. 6B illustrates a partial sectional view of top cover (150) without the nozzle insert (36) and FIG. 6A illustrates a partial sectional view of top cover (150) with the nozzle insert (36).

As illustrated in FIG. 6B, plug-shaped insert post (26) is disposed axis-symmetrically with fluid supply chamber (32). Insert post (26) preferably has a substantially planar end surface (28) adjacent its distal end has generally circular shaped. Insert post (26) can be a separate structure which may be attached to top cover (150) by a mechanical means (e.g., threaded, press fit or the like), but preferably be integrally formed with top cover (150) for simplicity of manufacture (such as by injection molding). Supply chamber (32) is generally forms an annulus which is bounded by post surface (30) and inside wall (34). Preferably, supply chamber (32) is adjacent to and in fluid communication with feed tube (23) to initially receive fluid from the storage container.

FIG. 6D and FIG. 6E illustrate an exploded view and a perspective view that best shows the interconnection between external components of dispensing unit (600). As illustrated dispensing unit (600) comprising a cylinder body (110), a top cover (150) and a fluid connection member (23).

Top cover (150) includes a circular protrusion (152) configured to plug and seal cylinder bore (111A). Top cover (150) further includes a socket (32) which providing housing for spray nozzle insert (36). Top cover (150) further includes an inlet bore (70) for insertion of the upper end (23A) of fluid supply member (23). Fluid supply member (23) includes an internal fluid passage (23B) for supplying fluid to the nozzle chamber (32). The diameter of fluid passage is typically 1, 2, 3 or 4 mm and its wall thickness is generally between 0.5 to 3 mm. The upper end of fluid supply member (23) may have thinner wall to allow certain radial expansion of section (23A) toward the inner wall of inlet bore (70) under fluid pressure. Top cover (150) further includes a spring-loaded check valve within housing (20) which provides a venting passage to the fluid container. Such venting passage serves to prevent vacuum buildup in the container as fluid being depleted. The venting check valve opens when the pressure differential between the interior of the container and the ambient pressure is greater than 20, 30 or 40 kPa. Top cover (150) further includes a socket (151) for storing gas canister (120). Socket (151) includes a pair of latching tabs (153) that retains canister (120) in any orientation of dispensing unit (600).

Fluid supply member (23) connects to the cylinder body through a ring (23B) that diametrically fits over the lower section (15) of cylinder body (110) to create a hermetically sealed fluid passage between section (15) and fluid supply member (23B).

FIG. 6E illustrates a perspective view of dispensing unit (600) which includes a locknut (160) configured to connect dispensing unit (600) with fluid container (not shown). Locknut (160) includes a soft gasket which serves to hermetic seal the interface of dispensing unit and the container. Universal S.P.I neck finish specification for standard closure with nominal diameter ranging from 13 mm to 120 mm may be used.

All pump components are provided of appropriate size and material to effectively create a seal therebetween when assembled. In this way there will be no gas or fluid leak between mating surfaces when the dispenser is pressurized or at rest. Although it is preferred that fluid or gas connection are sealed by simple frictional interaction, it will be understood that alternate means such as adhesive connections, ultrasonic welding, tapered locking or o-ring connection may be used;

FIG. 6F illustrates an attachment method of cylinder body (110) and top cover (150), It can be seem that top cover (150) includes four protruding bosses (141) each having a diameter of 3 mm and extending perpendicularly from the surface (150A) of top cover (150). Cylinder body includes two ears, the first ear (111) is visible and the second is at the far side and not visible in this view. Each ear includes a pilot hole (112) with oversized diameter relative to the bosses (141). Similarly, fluid passage (23) includes two ears (113) with similar pilot holes. When assembled, cylinder body and top cover are engages such that the four bosses (141) slip fit into pilot holes (112) and (113). Bosses (141) are extended 3 or 4 mm beyond the pilot holes to allow fir a thermoplastic staking punch to compress the extended end of the bosses. The stacking process creates radial expansion of the bosses which results in a permanent joint.

FIG. 7 and FIG. 7A, illustrate nozzle insert (36) in a side fontal and views respectively. It can be seen that the nozzle (36) has a cup-shaped cavity (38) with a cavity surface (39) and an end face (40). Located adjacent to end face (40) and generally concentric with the centerline of (38) is swirl chamber (42), illustrated with a chamber diameter CD. Swirl chamber (42) preferably has a generally conical shape for enhancement of flow efficiency.

A discharge orifice (44) having a predetermined orifice diameter (OD) is preferably located adjacent to and generally concentric with swirl chamber (42). Discharge orifice (44) thereby provides fluid communication between swirl chamber (42) and the ambient environment. As illustrated in FIG. 6E plurality of grooves (46) are disposed on end face (40) extending generally radially inward from cavity surface (39) to conical swirl chamber (42). In a preferred embodiment, each groove (46) connects generally tangentially with swirl chamber (42) and nozzle insert (36) has at least two spaced grooves (46). In the embodiment shown, nozzle insert (36) has three grooves (46) disposed in an equally spaced circular array about swirl chamber (42).

Referring back to FIG. 6A and FIG. 68 it can be seen that the inside wall (34) of supply chamber (32) is preferably sized to receive and frictionally retain nozzle insert (36). Preferably, the surfaces of inside wall (34) and insert surface (37) are sized such that when assembled in contact with each other, they will create an effective seal and there will be generally no liquid flow between the surfaces at 30 bar of pressure.

Nozzle insert (36) is fully assembled with inside wall (34) of top cover (150) such that end surface (28) and end face (40) are in contact, and forming a supply annular passage (50). Annular supply passage (50) is preferably formed between cavity surface (39) and post surface (30), and extends along at least a portion of the length of cavity surface (39) such that annular supply passage (50) is in fluid communication with both supply chamber (32) and one or more contiguous vanes (48).

Referring back to FIG. 7 and FIG. 7A, as illustrated, vanes (48) are defined by the surface (28) of insert post (26) and grooves (46) of insert (21). Each vane (48) has a resulting width W and height H which, in turn, defines a vane cross sectional area A in accordance with the equation:

A=W*H

Thus, the individual vane exit area EA of each vane exit (52) is the arithmetic product of exit width EW of that vane and height H, while the individual vane inlet area IA of each vane inlet (54) is similarly the arithmetic product of height H and the inlet width IW. For clarity inlet (54) the exit (52) are shown in the illustration by a thicker line. The cumulative vane inlet area for an atomizing is the summation of the individual vane inlet areas IA while similarly the cumulative vane exit area for an atomizing nozzle is the summation of the individual vane exit areas EA.

Preferred vanes (48) will feature a continuously inwardly decreasing width so that EW is generally less than IW while height H is generally constant over the length of each vane (48). Because the height H is preferably maintained generally constant over the radial length of vane (48), the ratio of the vane exit area EA to vane inlet area IA is generally equal to the ratio of the vane exit width EW to vane inlet width IW. Consequently, both ratios preferably define the narrowing conformation of each vane (48). This narrowing conformation preferably provides a continuously accelerating liquid flow within each vane (48) as the liquid traverses each vane (48) in a direction from supply chamber (32) toward swirl chamber (42).

Although it is preferable that the width of each vane (48) continuously decreases inwardly from cavity surface (39), the spray characteristics of liquid dispensed from nozzles are generally insensitive to the amount of decrease in the vane width W. Thus, the ratio of the vane exit width EW to the vane inlet width IW, and likewise the ratio of vane exit area EA to the vane inlet area IA (if vane height is constant), may vary in a range from about 0.10 to about 1.0.

The proper dimensioning of the cross sectional exit area EA of vanes (48) in cooperation with the proper sizing of chamber diameter CD or orifice diameter OD is critical to achieving the spray characteristics. The Sauter Mean Diameter of a given spray generally decreases according to the following equation, and as graphically illustrated in FIG. 8

SMD=44.6−57.1*(CD*EA)

Where SMD=Sauter Mean Diameter (microns)

CD=Chamber diameter for values generally in a range of between about 0.5 mm and about 1.5 mm

EA=Individual vane exit area for values generally in the range of between about 0.02 mm²and about 0.07 mm².

Although FIG. 8 indicates a generally decreasing particle size as individual vane exit area EA and/or chamber diameter CD increase, data generally indicates that the Sauter Mean Diameter of a resulting spray was found to generally increase if the individual vane exit area EA is about 0.12 mm²and chamber diameter CD is about 2.0 mm.

Based on the foregoing relationships, the preferred embodiments will have a cumulative vane exit area (i.e., a summation of the individual vane exit areas EA) in a range of between about 0.18 mm²and about 0.36 mm²and generally a chamber diameter CD in a range of between about 1.3 mm and about 2.0 mm, and most preferably the chamber diameter CD being in a range of between about 1.4 mm and about 1.5 mm. It has been suggested by U.S. Pat. No. 5,711,488 that such embodiments will generally produce a spray being in the range of between about 38 microns to about 43 microns with a liquid pressure being in the range of between about 11 bar to about 14 bar. U.S. Pat. No. 5,711,488 is hereby incorporated by reference.

In operation, liquid product is provided from a container through feed tube (23) under pressure created by the pressure-multiplying pump. The fluid, upon exiting feed tube (23) enters supply chamber (32) whereupon it enters supply annular passage (50). The pressurized liquid then passes through supply annular passage (50) and is directed into the plurality of vanes (48). Although it is preferred that teed tube (23), supply chamber (32) and supply annular passage (50) cooperate to transport the liquid from the container to the plurality of vanes (48). Preferably, the liquid is continuously accelerated by the decreasing cross sectional area A of each vane (48) which directs the liquid radially inward toward swirl chamber (42). The accelerated liquid preferably exits the vanes (48) generally tangentially into swirl chamber (42), and the rotational energy imparted to the liquid by each vane (48) and the tangential movement into swirl chamber (42) generally creates a low pressure region adjacent the center of swirl chamber (42). This low pressure region will tend to cause ambient air or gas to penetrate into the core of swirl chamber (42). The liquid then exits swirl chamber (42) as a thin liquid film (surrounding aforementioned air core) and is directed through discharge orifice (44) to the ambient environment. Upon discharge, inherent instabilities in the liquid film cause the liquid to break into ligaments and then discrete particles or droplets, thus forming an atomized spray.

As illustrated in FIG. 9, the preferred embodiment of the present invention generates an atomized spray of liquid particles or droplets having a mean particle size of about 36 microns at a fluid pressure of around 13.8 bar when used to dispense a fluid having a viscosity of about 10 centipoises. In one embodiment the diameter of the swirl chamber is 1.5 mm, the orifice diameter is 340 micron, and the cumulative vane exit area is about 0.9 mm.

While the structure of the nozzle is not intended to be limited to the dispensing of any specific product or category of products, it is recognized that the structure of the spray nozzle which includes the pressure multiplying pump is particularly efficient and applicable for the dispensing, at pressures from about 11 bar to 30 bar, of liquid products having a viscosity, density, and surface tension generally about 10 centipoise, 25 dynes per centimeter respectively with disregard to the application. The structure of the present invention may be used in for dispensing a cosmetic spray, household, industrial spray or the like. It will be understood by one skilled in the art, however, that deviation from these values for appropriate different applications and/or for dispensing of various liquids and viscosities should be possible without affecting the spray characteristics of the present invention. For example, the viscosity of the liquid to be dispensed may vary from about 5 cps to 20 cps without deviating from the scope of this invention.

The foregoing description of the preferred embodiments of the invention has been presented for purposes of illustration and description. It is not intended to be exhaustive or to limit the invention to the precise form disclosed. Modifications or variations are possible and contemplated in light of the above teachings by those skilled in the art, and the embodiments discussed were chosen and described in order to best illustrate the principles of the invention and its practical application, and indeed to thereby enable utilization of the invention in various embodiments and with various modifications as are suited to the particular use contemplated. It is intended that the scope of the invention be defined by the claims appended hereto.

Number	Date	Country
61963421	Dec 2013	US
61962953	Nov 2013	US
61960072	Sep 2013	US
61851415	Mar 2013	US

PRESSURE MULTIPLYING AEROSOL PUMP

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CPC

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CROSS-REFERENCE TO RELATED APPLICATIONS

Provisional Applications (4)