HK1036773B - A vortex system for nebulizing a liquid for inhalation and a method for nebulizing - Google Patents

Description

Vortex system for atomizing inhalation liquid and atomization method

RELATED APPLICATIONS

The present application is a continuation of U.S. patent application No.90/40666, entitled "fluid treatment system and method," filed 3/18/1998, which is incorporated herein by reference.

Technical Field

The present invention relates to a device for vaporizing and homogenizing a fluid, and to a system for vaporizing and homogenizing a fluid. And more particularly to medical devices and systems for producing finely homogenized or vaporized gas phase fluid mixtures.

Background

Heretofore, various types of devices have been developed for converting liquids or mists into vapor phase fluids. Many devices of this type have been used to produce internal combustion engine fuel. In order to optimize fuel oxidation in the engine combustion chamber, the fuel/air mixture typically must be further vaporized or homogenized to obtain a stoichiometric gas phase mixture. Ideal fuel oxidation results in more complete combustion and lower pollution.

More specifically, for internal combustion engines where stoichiometric is a condition that provides the amount of oxygen necessary to completely combust a given amount of fuel, and where the oxygen is in a homogeneous mixture, optimal correct combustion is achieved without residue left from incomplete or inadequate oxidation. Ideally, the fuel should be completely vaporized, mixed with air, and homogenized before entering the combustion chamber for proper oxidation. In conventional internal and external combustion engines, the unvaporized fuel droplets are generally not able to ignite and completely burn, creating problems with combustion efficiency and pollution.

Another problem, unlike the use of swirl flow technology in internal combustion engines, involves the problem of extreme vaporisation of different medicaments inhaled by the inhaler. Typical inhalers produce a liquid/gas mixture of the medicament for direct inhalation into the lungs. However, it is difficult to achieve high vaporization of the drug in order to get the drug directly into the blood through the lungs. That is, the residual excess drug remains liquefied, rather than being further broken down into smaller molecular size particles, for immediate passage through the lungs into the blood. Therefore, there is a need to develop a vaporization device that will further vaporize and homogenize the liquid/gas mixture into a vapor consisting of vapor particles small enough to pass the drug directly into the blood through the lungs.

In the swirl chambers used in prior art devices, fluid is introduced into the gas which is swirled through the cylindrical chamber. These vortex chambers have smooth cylindrical inner walls. This smooth vortex chamber inner wall configuration may limit the degree of turbulence within a given vortex chamber and the effective vaporization rate of the vortex chamber.

Another significant disadvantage of the known devices is that they do not compensate for the pressure difference between the different inlets to the vortex chamber. As the gas/fluid mixture passes through the different vortex chambers, additional gas enters each chamber tangentially, causing a pressure differential between the different inlets. Since ambient air enters the vortex chamber at all inlets, it is difficult to maintain the air/fuel ratio of the mixture as it passes through the vortex chamber.

Yet another aspect of the pressure differential problem of previously known devices is that swirl chambers near the low pressure end of the flow passage (e.g. near the engine intake) have a higher advantage than other swirl chambers by virtue of the greater flow available. This problem is particularly noticeable and problematic during engine acceleration. When the swirl chamber at the low pressure end of the flow passage dominates the other swirl chambers, the efficiency of the other swirl chambers is greatly reduced.

Previous centrifugal atomization devices also have certain limitations such as being too bulky to effectively introduce fluid tangentially into the centrifugal chamber, unnecessarily inhibiting the suction of engine intake vacuum, and unevenly discharging the centrifugal flow into the engine intake.

Yet another problem with previous swirl vaporisation devices is that they do not take advantage of or take advantage of the fact that the swirl chamber output orifice is adjustable and the diameters of adjacent chambers are different.

In view of the above, there is a need for a centrifugal vortex system that addresses or alleviates the above-mentioned limitations of known prior devices. Centrifugal vortex systems have been developed that have a vortex chamber with better turbulence in the chamber, more complete breakdown of the liquid into smaller sized vapor fluid particles, and correct for flow through different orifices in the vortex chamber walls. In addition, there is a need for a centrifugal vortex system that better pre-mixes air and fuel prior to the gas/fuel mixture entering the vortex chamber. There is also a need for an alternative small volume centrifugal device to better mix, vaporize, homogenize smaller size molecular vapor particles, and expel the particles from an inhaler-type drug delivery device (and to/from other desired uses) to the intake of an engine.

Disclosure of Invention

It is an object of the present invention to provide a vortex chamber having more optimized turbulence and substantially eliminating the formation of liquid trajectory rings on the inner wall of the vortex chamber.

It is another object of the present invention to provide a vortex chamber housing having a stepped inner wall surface to increase the turbulence of the fluid as it flows through the vortex chamber.

It is another object of the present invention to provide a vortex chamber having an irregular or textured inner wall surface to increase the turbulence of the fluid as it flows through the vortex chamber.

It is another object of the present invention to provide a pressure differential source, such as a tapered inlet passage that may be formed by a sleeve, that equalizes the flow into several inlet orifices of a swirl chamber.

It is another object of the present invention to provide a series of tangential baffles on a centrifugal chamber to form a series of tangential channels into the chamber to enhance the centrifugal flow of fluid in the chamber.

Another object of the invention is to increase the turbulence of the vortex chamber by reducing the volume of the chamber and by making the height of the vertical walls of the centrifugal chamber smaller than the maximum inner diameter of the venturi tube to which it is connected.

It is a further object of the present invention to obtain optimum turbulence in one vortex chamber and to provide for swirl flow rotation in alternative, opposite rotational directions as it flows from one vortex chamber to an adjacent vortex chamber, thereby enhancing vaporization.

It is yet another object of the present invention to provide a device for medical use that is capable of breaking down a vapor/gas mixture into smaller, molecular size particles. It is yet another object of the present invention to create a device that breaks down the vapor/liquid mixture into particles of extremely small size so that the particles can pass immediately and directly through the lungs into the person's blood.

To achieve the above object, the present invention provides a vortex system for atomizing an inhalation liquid, comprising: a venturi element in fluid communication with a source of compressed gas and also in fluid communication with said source of fluid; a vortex element comprising: a chamber housing enclosing a vortex chamber, in fluid communication with the venturi element, for generating a rotational flow in the vortex chamber and atomizing the liquid; a plurality of apertures in the chamber housing to enable fluid to be input tangentially into the vortex chamber to create a rotational flow in the vortex chamber; a chamber outlet in fluid communication with the vortex chamber to allow fluid to be expelled from the vortex chamber.

The present invention also provides a vortex system for atomising an inhaled liquid comprising: an eddy current element comprising: a chamber housing enclosing a vortex chamber in fluid communication with a source of compressed gas and with the source of liquid, creating a vortex in the vortex chamber and atomizing the liquid; a plurality of apertures in the chamber housing to enable fluid to be input tangentially into the vortex chamber to create a rotational flow in the vortex chamber; a chamber outlet in fluid communication with the vortex chamber to allow fluid to exit the vortex chamber; and a decelerating element in fluid communication with the chamber outlet.

In one embodiment, the inner wall of the vortex chamber housing is stepped or textured, or both, to enhance fluid turbulence through the vortex chamber. In another embodiment, a multi-stage vortex chamber is used.

In another embodiment, a velocity reduction chamber is fluidly connected to at least one vortex chamber, the velocity reduction chamber providing complete homogenization of the gas/fluid mixture and also for fluid separation when the present invention is used for fluid separation, such as desalination.

Other objects, features and advantages of the present invention will become more apparent from the following detailed description of the invention when taken in conjunction with the accompanying drawings.

Drawings

With reference to the following drawings, preferred embodiments of the present invention are described below,

FIG. 1 is a top cross-sectional view of a centrifugal vortex system of the present invention.

FIG. 2 is a side cross-sectional view of the centrifugal vortex system of FIG. 1 taken along line 2-2.

Fig. 3 is an enlarged exploded sectional view of the vaporization section of fig. 1.

Fig. 4 is a top view of the injector plate of fig. 1.

Fig. 5 is a cross-sectional view of the injector plate of fig. 4 taken along line 5-5.

Fig. 6 is a bottom view of the injector plate of fig. 1.

Figure 7 is a side cross-sectional view of another embodiment of the vortex structure of the present invention.

FIG. 8 is a bottom cross-sectional view of the inlet differential pressure source arrangement of the vortex chamber assembly of FIG. 7 taken along line 8-8.

Figure 9 is a side cross-sectional view of the inlet differential pressure source arrangement of the vortex chamber assembly of figure 8 taken along line 9-9.

Figure 10 is a top view of the inlet differential pressure source configuration of the vortex chamber assembly of figure 8.

Figure 11 is a bottom cross-sectional view of another embodiment of a vortex chamber assembly inlet differential pressure source configuration of the present invention.

Figure 12 is a side cross-sectional view of the inlet differential pressure source configuration of the vortex chamber assembly of figure 11 taken along line 12-12.

Figure 13 is a top view of the inlet differential pressure source configuration of the vortex chamber assembly of figure 11.

Figure 14 is a perspective view of an alternative embodiment of the vortex chamber housing of the present invention.

Figure 15 is a cross-sectional view of another alternative embodiment of the vortex chamber housing of the present invention.

Figure 16 is a cross-sectional view of yet another alternative embodiment of the vortex chamber housing of the present invention.

Figure 17 is a perspective view of another alternative embodiment of the vortex chamber housing of the present invention.

FIG. 18 is a cross-sectional elevation view of an alternative embodiment of a venturi of the present invention.

FIG. 19 is a partial cross-sectional view of an alternative embodiment of the venturi of the present invention of FIG. 18, taken along line 25-25.

FIG. 20 is a sectional elevation view of another alternative embodiment of a centrifugal vortex chamber of the present invention for vaporizing a fluid.

Fig. 21 is an enlarged partial cross-sectional view of the embodiment of fig. 20.

FIG. 22 is a cross-sectional elevation view of another alternative embodiment of the multi-stage centrifugal vortex system for vaporizing a fluid of the present invention.

FIG. 23 is a cross-sectional exploded view of another alternative embodiment of a single stage centrifugal vortex system for vaporizing a fluid in accordance with the present invention.

FIG. 24 is a cross-sectional elevation view of another alternative embodiment of a single stage centrifugal vortex system for vaporizing a fluid in accordance with the present invention.

Fig. 25A-C are bottom, side and top views of the input mixer of the embodiment of fig. 24.

Fig. 26A-C are bottom, side and top views of the processor of the embodiment of fig. 24.

Fig. 27A and 27B are cross-sectional elevation views of an alternative nozzle to the embodiment of fig. 24.

Detailed Description

In the present context, the terms "homogenisation", "vaporisation" or other words derived from these terms mean the transformation of a liquid from a suspended or vaporous state to a gaseous phase by turbulent swirling flow, where conditions of high velocity, low pressure, high vacuum, i.e. pressure differential, exist.

Figures 1 through 6 illustrate a first embodiment of a centrifugal vortex system 30 of the present invention. As shown in FIG. 1, the centrifugal vortex system 30 has three parts: a fuel vaporization section 32, a main air section 34 and a centrifugal section 36. The fuel vaporization section 32 is shown with two fuel injectors 38 mounted in bores 40 of an injector plate 42. The fuel injectors 38 may comprise conventional electronic fuel injectors, and preferably have an injection angle of 30 ℃.

Within the fuel vaporization section 32 is a premix chamber 44, and fuel is injected into the premix chamber 44 from an outlet 46 of the fuel injector 38. Ambient air also enters the pre-mix chamber 44 through an ambient air duct 50 and mixes with fuel injected by the fuel injectors 38. The premixing chamber 44 is defined in part by the outer surface 52 of the swirl chamber housing 54 and the outer surface 68 of the tapered extension 58. The pre-mix chamber 44 is also defined by the inner surface 56 of the differential pressure source sleeve 60. The purpose and function of the sleeve 60 and the vortex chamber housing 54 will be discussed in detail below.

The swirl chamber housing 54 includes: the outer surface 52, the inner wall surface 62 and the bottom surface 63 of the chamber. In addition, the swirl chamber housing 54 also includes a tapered extension 58 for increasing fluid flow in the pre-mix chamber 44, which is secured to the injector disk 42 by screws 48 (FIG. 3) inserted through holes 49. The inner wall surface 62 of the swirl chamber encloses a swirl chamber 64 which can generate a swirling flow of the fluid. The swirl chamber housing 54 has an array of apertures 66 which enter the housing at an angle to allow fluid, such as an air/fuel mixture, to enter the swirl chamber 64 in a tangential direction. The vortex chamber top edge 61 abuts the inner surface 55 of the jacket top. A conventional gasket (not shown) is preferably interposed between the edge 61 and the top surface 55 to prevent fluid from leaking between the edge 61 and the surface 55 into the vortex chamber 64.

As shown in FIG. 3, the array of holes 66 are arranged in a plurality of rows R and a plurality of columns C around the vortex chamber to increase the swirl turbulence through the chamber 64. Preferably, the rows R and columns C are relatively staggered or offset in the circumferential direction. By staggering the rows and columns in the array of holes 66, the tendency of the fluid to break up into discrete orbital rings in the vortex chamber 64 is eliminated or at least substantially reduced. In addition, the orientation of the holes also provides a significant increase in turbulence (and vaporization efficiency) within a given vortex chamber.

A conical sleeve 60 located around the vortex chamber housing 54 forms a differential pressure source arrangement. As shown, the sleeve 60 includes a portion 75 of varying thickness which causes the diameter of the tapered inner surface 56 to increase. The sleeve 60 terminates in an edge 57. The sleeve 60 also includes an outlet 70 through which fluid exits after being processed in the swirl chamber 64. The outlet 70 is bounded by a cylindrical surface 71, the cylindrical surface 71 and the jacket top surface 55 meeting at a rounded corner 73. The sleeve inner surface 56 is shown as having a smallest diameter at the end proximate the sleeve outlet 70. The inner surface 56 of the sleeve increases in diameter toward the edge 57. While the surface of varying diameter generally includes a tapered inner surface 56, it will be appreciated that a stepped inner surface will also work effectively.

The varying diameter jacket inner surface 56, when positioned around the vortex chamber housing 54, forms a varying width gap 72 with the vortex chamber housing outer surface 52. As shown in fig. 3, the width is changedThe gap of formation is in d₁Has a smaller width at d₂The width of the bit is larger. The varying width gap 72 creates a varying pressure differential across the orifices 66 in the vortex chamber housing 54 and has a stronger restrictive effect on the flow rate of the orifices 66 near the outlet 70 than the orifices farther from the outlet 70. Thus, depending on the position of the apertures 66 relative to the sleeve outlet 70, different pressure differences may be created as fluid enters through different apertures 66. In operation, the bore 66 closest to the outlet 70 has a higher pressure because this end includes the low pressure end of the fuel vaporization section 32.

By providing a variable pressure supply structure, such as a sleeve 60, around the bore 66 of the swirl chamber housing 54, the fluid flow into the different bores can be made substantially equal. Substantially equal fluid flow through the different orifices 66 may increase the efficiency and effectiveness of the swirl chamber 64.

As shown in fig. 1, the sleeve 60 and the vortex chamber housing 54 are mounted in a fuel vaporization housing 74 having an inner surface 76. More specifically, a top exterior surface 79 (FIG. 3) of the sleeve 60 is proximate to a top interior surface 77 of the fuel vaporization housing 74. The fuel vaporizing housing inner surface 76 and the outer surface 68 of the conical extension 58 enclose the ambient air conduit 50 described above.

The injector disk 42 is shown in fig. 1, 3, 4, 5 and 6. The bottom surface 47 of the injector plate 42 has a pair of holes 40 for receiving the fuel injectors 38 (FIG. 1). The injector disk 42 also includes a first shoulder 39 and a second shoulder 41 (see fig. 4 and 5). The first shoulder 39 is connected to the connector 43 and the second shoulder 41 is connected to the rim 57 (fig. 1). Cylindrical central extension 45 is connected to conical extension 58 (fig. 1) by set screw 48.

As shown in fig. 1 and 2, the main air portion 34 includes: a main air housing 80, a venturi body 82 and a conventional butterfly throttle plate 84. At one end of the main air section 34 is an air inlet 86. It leads to an inner cylindrical portion 90 having an annular inner surface 92.

The conventional throttle plate 84 is hingedly secured within the inner cylindrical portion 90. The throttle plate 84 is mounted on a rotatable central shaft 96, the central shaft 96 being perpendicular to the direction of flow F of air in the hollow interior 90. Rotation of the shaft 96 may adjust the inclination of the throttle plate 84 within the hollow interior 90 to vary the air volume and thus the air/fuel mixture entering the engine.

There is an ambient air passage 100 in the main air housing 80. The air passage 100 communicates with a slot 94 in the main air housing 80. The ambient air ducts 102 and 50, in turn, pass air into the pre-mix chamber 44 through the air passage 100 and the slot 94.

Also mounted within the primary air section 34 is a venturi 82 including an inlet 104, a plurality of elongated apertures 106 and a venturi outlet 110. Additionally, the venturi 82 also includes a venturi outer surface 112 and an inner surface 114. As shown, the diameter of the venturi inner surface 114 is greatest at the venturi inlet 104 and outlet 110. The diameter of the venturi inner surface 114 is substantially the same at the venturi inlet 104 and the venturi outlet 110. In contrast, the diameter of the venturi inner surface 114 is smallest at the venturi throat 116. An annular step is formed on the inner surface 114 adjacent the venturi throat 116.

The primary air portion 34 also includes an annular cross-sectional edge 122 (shown in FIGS. 1 and 2) that intersects the annular inner surface 92 at an annular outer corner 124. The edge 122 also intersects the annular face 126 at an annular inner corner 130. In addition, the annular surface 126 also intersects the profile edge 132 at an annular angle 134. The outer surface 112 of the venturi 82 is secured at the surface 126 by bonding, interference fit, or any other conventional means such that the venturi 82 is located in the main air portion adjacent the annular surface 126.

In the primary air intake portion 34 is an intermediate mixing chamber 136 (fig. 1) which imparts a turbulent mixing to the fluid exiting the sleeve outlet 70 by rotating it cylindrically before entering the venturi 82 through the elongated orifice 106. The intermediate mixing chamber 136, which further vaporizes and homogenizes the fluid, is defined by annular surface 126 and annular cross-sectional surface 140 interconnected at an angle 142. The centrifugal portion 36 is connected to the main air portion 34 at a cross-sectional edge 132.

Fluid exiting the venturi outlet 110 enters the centrifuge section 36 through the inlet 144. The centrifuge section 36 generally comprises: a centrifugal housing 142, an inlet 144, an inlet chamber 146, a series of baffles 150 in a tangential direction with respect to a centrifugal chamber 152, and a plurality of outlet channels 154. As shown, the centrifuge housing is of a substantially cylindrical configuration having a vertical annular wall 156 interrupted by the inlet 144. The wall 156 is integral with the top wall 160 (fig. 2).

As shown in fig. 2, a hub portion 162 extends downwardly from the centrifuge top wall 160. Hub portion 162 has an inner surface 164 and an outer surface 165, and they are substantially parabolic. As will be discussed in more detail below, hub portion 162 actually reduces the volume of chamber 152 and enhances the circular centrifugal fluid flow within chamber 152 around hub portion 162.

Opposite the top wall 160 in the centrifugal chamber 152 is a contoured bottom liner 166. The bushing 166 includes a contoured top surface 170 and a bottom surface 172. The top surface has an annular flat portion 174, an upwardly curved portion 176 and a conical central portion 180.

As mentioned above, the inlet chamber 146 of the centrifuge section 36 also houses a series of tangentially oriented baffles 150. Each guide vane 150 includes: a leading end surface 184, a medial corner 186, and a rounded trailing end 190. A guide surface 192 is formed between the front face 184 and the corner 186. A flat surface 194 is formed between the leading end surface 184 and the trailing end 190. Finally, a surface 196 is formed between the corner 186 and the trailing end 190.

The guide vanes 150 are arranged relative to each other in order to create a plurality of tangential fluid passages 200 between adjacent guide vane 150 surfaces. In addition, a tangential channel 202 is formed between the surface 194 of the baffle 150 and the adjacent vertical wall 206 in the inlet chamber 146. Furthermore, a tangential channel 204 is formed between the surface 192 of the baffle 150 and the adjacent vertical wall 210 in the inlet chamber 146.

As shown in FIG. 1, each rear face 194 forms a tangential angle with the annular wall 156 of the centrifuge section 36. Thus, fluid enters chamber 152 through channels 200, 202, and 204 substantially tangentially to annular wall 156 to enhance annular centrifugal flow in chamber 152.

To secure the centrifuge housing 142 to an engine intake (not shown), mounting locations 212, 214, 216 in the centrifuge housing enable fasteners, such as bolts 180 (FIG. 2), to secure the centrifuge housing 142 to the engine via the attachment plate 143.

Fig. 7 illustrates an embodiment of the present invention. It shows a vortex chamber assembly 220, which generally comprises: a conventional electronic fuel injector 222, a first swirl chamber housing 224 and subsequent swirl chamber housings 226, 228, 230, 232. Each vortex chamber housing 226 and 232 receives fluid discharged from a preceding vortex chamber housing. For example, the vortex chamber housing 228 receives fluid flowing in from an outlet of the vortex chamber housing 226, and the like.

Fuel injectors 222 are mounted in bores 234 of injector disc 236. Each fuel injector has an outlet 240 for injecting fuel into the premix chamber 242. Ambient air is charged into the pre-mix chamber 242 through an ambient air conduit 244. The structure and function of the pre-mix chamber 242 and the ambient air duct 244 are similar to the structure and function of the pre-mix chamber 44 and the ambient air duct 50 of FIG. 1.

The vortex chamber housings 224, 226, 228, 230, and 232 define vortex chambers 248, 250, 252, 254, and 256, respectively. Each vortex chamber housing 224-232 has an array of apertures 260-268. Each of the aperture arrays 260-268 are arranged in a plurality of rows and a plurality of columns, similar to that shown in fig. 3. In addition, the staggered arrangement of each array of orifices may enhance the vertical turbulence through the various vortex chambers 248-256.

Conical jackets 272, 274, 276, 278 and 280 located around the vortex chamber housings 224, 226, 228, 230 and 232 form the respective differential pressure source inlets. Each differential pressure source inlet functions in a manner similar to the sleeve 60 of fig. 1. Each sleeve 272 and 280 has an inner surface 284, 286, 288, 290 and 292, respectively. The inner surfaces 284 and 292 of each sleeve respectively include: a fixed diameter portion 296, 298, 300, 302, 304 and a varying diameter inner surface portion 308, 310, 312, 314, 316. Each vortex chamber housing 224, 226, 228, 230, and 232 has an outer surface portion 318, 320, 322, 324, and 326, respectively. Gaps 330, 332, 334, 336 and 338 of varying sizes are formed between surfaces 330 and 338 and surfaces 308 and 316, respectively. Thus, the varying size of the gaps allows the apertures 260 and 268 to have different pressures depending on the location of the apertures 260 and 268, which function in a manner similar to the gaps 72 (FIGS. 1 and 2).

In addition, each sleeve 272 and 280 has an outlet 340 and 348, respectively, which are in fluid communication with the subsequent vortex chamber. Fig. 8-10 show the sleeve 278 and swirl chamber 254 in greater detail. Each of the outlets 340 and 348 is a U-shaped slot, as indicated by numeral 349 in fig. 9 and 10. The outlets 340, 268 are in fluid communication with the subsequent mixing chambers 350, 352, 354, and 356, respectively, so the apertures 262, 268 receive fluid from the outlets 340, 346 to maintain a substantially constant air second fluid mixture because no additional air is introduced as the fluid flows through the swirl chamber 250, 256. In addition, each vortex chamber housing 224-232 has a conical base portion 358 to enhance the mixing and swirling properties through the mixing chambers 242, 350, 352, 354 and 356.

To install fasteners (not shown), the sleeves 274 and 280 each have a hole 368 therein, such as with a conventional set screw, to secure the lower portion 370 of the sleeve to the upper portion 372 of the previous sleeve or to the vaporization housing 374.

Figures 11 to 13 show another embodiment of a suite assembly for use in a plurality of vortex chambers as shown in figure 7. More specifically, the illustrated sleeve 376 has a fixed diameter inner surface 377, a variable diameter inner surface 378, an outlet 379, and an outlet bore 381. The illustrated vortex chamber housing 383 has a plurality of angled holes 385 and opens tangentially into the vortex chamber 387. A variable clearance gap 389 is formed between the inner surface 378 of the sleeve 376 and the outer surface 391 of the swirl chamber 383.

Figure 14 shows a further embodiment of a vortex chamber of the present invention. The vortex chamber housing 380 has an outer surface 382 and an inner chamber wall 384 that defines a vortex chamber 386. To increase the turbulence of the swirl in the swirl chamber 386 and to break down any unvaporized particles in the swirl into smaller particles, a step 388 is formed on the chamber inner wall 384. As shown, each step 388 includes a chamfer 390 and a cross-section 392. There are also a plurality of apertured ramps 394 on the vortex chamber housing 380 that intersect the chamber inner wall 384 at cross-sections 392. As the fluid passes through the vortex chamber 386, the step 388 creates a smaller vortex adjacent the different cross-sections 392, which facilitates increasing the turbulence through the vortex chamber 386.

As an alternative or additional way of increasing the turbulence of the swirling flow in the swirl chamber 386 and further breaking up any unvaporized droplets in the swirling flow into smaller droplets, and enhancing the vaporization of the unvaporized droplets, the chamber inner wall 384 may comprise a textured surface. The inner wall may be formed with a textured or irregular surface by sandblasting (heavy grit) or using a glass bead. Textured or irregular chamber interior wall surfaces may cause the liquid to pass through the vortex chamber 386 in a more turbulent manner. When the unevaporated droplets impact the textured inner wall surface, they spread out and break up into smaller droplets. Vaporization is also easier than with a smooth inner wall surface.

Figure 15 shows another embodiment of a vortex chamber assembly of the present invention. The vortex chamber housing 570 includes an outer surface 572 and inner surfaces 574, 576, 578, 580, and 582. Each of the inner surfaces 574-582 is substantially cylindrical and defines vortex chambers 584, 586, 588, 590 and 592, respectively.

The apertures 594 are arranged in staggered rows and columns and are tangentially distributed in the vortex chamber housing 570 to provide tangential entry of fluid into each of the vortex chambers 584 to 592. This tangential entry of fluid creates a turbulent swirling flow through the vortex chamber, and in the swirling flow breaks the fluid into smaller droplets and vaporizes the remaining liquid droplets. As shown, the apertures 594 are arranged in a plurality of rows and columns, preferably staggered with respect to one another, to further enhance the turbulence characteristics of the fluid passing through the vortex chambers 584-592.

The cylindrical outlet flange 596 includes an outer surface 598 and an inner surface 600. The outlet flange is connected to the upstream end 602 of the vortex chamber housing 570. The inner surface 600 encloses an outlet of the vortex chamber 584 in the vortex chamber housing 570. As shown, the diameters of the vortex chambers 584-592 decrease in sequence. That is, the diameter of inner surface 582 is smaller than the diameter of inner surface 580. In turn, inner surface 580 has a diameter that is less than a diameter of inner surface 576, and inner surface 576 has a diameter that is less than a diameter of inner surface 574. Given this construction, the tendency of the swirl chamber nearest the low pressure end (swirl chambers 584 and 586) to receive more flow through the orifice 594 than the swirl chambers nearest the high pressure end 606 (swirl chambers 590 and 592) is greatly reduced as fluid passes through the swirl chambers 584-592 in a swirling manner, wherein a low pressure end is formed at the outlet 604 and a high pressure end is formed near the upstream end 606.

In addition, a nozzle 608 (FIG. 15) of suitable size is mounted at the upstream end of each vortex chamber 584, 586, 588 and 590, respectively, to enhance fluid vaporization as the fluid passes through the vortex chambers 584-592. The nozzle 608 subjects the vapor passing through the vortex chamber to an additional pressure differential, thereby enhancing vaporization and breakup of the fluid droplets. The nozzle 608 is preferably sized to be secured in the upstream end of the swirl chambers 584-590 by an interference fit.

Fig. 16 shows another embodiment of the present invention. As shown, figure 16 shows a vortex structure 611 containing a vortex chamber housing 612, the vortex chamber housing 612 having an outer surface 614 and inner surfaces 616, 618, 620, 622 and 624. The inner surfaces 616-624 are substantially cylindrical and define vortex chambers 626, 628, 630, 632, and 634, respectively. Apertures 636 are formed tangentially relative to the inner surfaces 616-624 of the vortex chambers 626-634. The orifices 636 are distributed in an array in the vortex chamber housing 612 which causes the fluid to flow tangentially into the vortex chambers 626-634. The fluid flows tangentially through the vortex chamber to generate a vortex, which breaks up the droplets in the vortex into smaller droplets and further vaporizes or homogenizes the droplets.

A cylindrical outlet flange 640 is connected to one end 642 of the vortex chamber housing 612. Outlet flange 640 includes an inner surface 644 and an outer surface 646. Outlet flange inner surface 644 circumscribes outlet 648. Outlet flange 640 is similar to outlet flange 596 (fig. 15) except that inner surface 644 has a smaller diameter than inner surface 600 of outlet flange 596 (fig. 15). In addition, the outlet flange 640 has a hole 650 into which a screw (not shown) is selectively inserted to adjust the flow resistance through the outlet flange 640. As the swirl flow passes through the outlet 648, the greater the resistance to airflow caused by the swirl flow if the screw is inserted deeper into the outlet 648.

In general, the air resistance of the vortex structure can be varied by varying the diameter of the outlet orifice and/or varying the diameter of the passage between adjacent vortex chambers in the vortex structure. The embodiment of figure 15 shows a relatively large outlet and relatively small passages between adjacent vortex chambers formed by the presence of the nozzles 608. In contrast, the embodiment of figure 16 shows a smaller outlet and a larger passage between the vortex chambers. In some applications, the embodiment shown in FIG. 16 has been found to be superior to the embodiment shown in FIG. 15.

Figure 17 shows another embodiment of the vortex chamber housing of the present invention. This embodiment illustrates a vortex chamber housing 940 that generally includes a bottom wall 942 and a vertically extending cylindrical wall 944. The cylindrical wall 944 includes an inner surface 946, a top edge 947 and an outer surface 948. The inner surface 946 and the bottom wall 942 define a vortex chamber 952. The vortex chamber housing 940 operates in a similar manner to the vortex chamber housing 54 shown in figure 1.

From the outer surface 948 to the inner surface 946 are a series of elongated tangential slots 950 through the wall 944 which provide tangential entry of the fluid into the vortex chamber 952 relative to the swirling flow in the chamber. Each slot 950 is shown as extending from the top edge 947 of the wall 944 all the way to the vortex chamber housing bottom wall 942 with no interruption in the middle. The slots 950 are distributed tangentially to the cylindrical inner surface 946 of the annular wall 944, allowing fluid to enter the vortex chamber 952 of the vortex chamber housing 940 in a tangential direction to the swirling flow.

Tangential entry of fluid into the vortex chamber 952 through the elongated slots 950 creates a continuous layer of motive fluid that rapidly passes through the vortex chamber inner surface 946 adjacent each slot 950. This substantially prevents non-vaporized droplets of fluid from collecting on inner surface 946. When droplets of unvaporized fluid approach or contact the inner surface 946, the droplets are blown off of the inner surface by droplets of fluid that pass through the slots 950 and enter the vortex chamber 952. Any number of slots 950 may be used to achieve the desired result. In addition, different widths of the slots 950 may also be used. The slots 950 in the annular wall 944 may be obtained by laser, circular saw, or any other suitable method. For example, the slot 950 may be about 0.254mm (0.01 inch) wide.

Fig. 18 and 19 show another embodiment of the venturi of the present invention. The venturi 954, as shown in this embodiment, includes a housing 956 and a series of tangential apertures 958 opened in the housing 956. The tangential bore extends from the outer surface 955 of the housing to the inner surface 957 of the housing. Apertures 958 are formed tangentially within housing 956 such that a fluid, such as an air/fuel mixture, enters venturi interior 960 tangentially through apertures 958, thereby increasing the turbulence of the fluid passing through venturi 954.

As shown, the tangential apertures 958 open into a narrow throat 959 of the venturi 954. At the narrow throat 959, the velocity of the fluid F through the venturi 954 is greatest. The turbulence and mixing of the two fluids is enhanced by introducing the second fluid into the venturi interior 960 through the tangential apertures 958 of the narrow throat 959. Introducing the second fluid into the venturi interior 960 through the tangential apertures 958 causes the fluid passing through the venturi interior 960 to swirl, thereby increasing the turbulence of the fluid. The increased turbulence of the fluid passing through the venturi 954 further enhances the vaporization and homogenization of the fluid passing through the venturi 954. Thus, as the fluid flow F passes through the venturi from the venturi inlet 962 to the venturi outlet 964, the fluid flow intersects the tangential flow of the second fluid. A second fluid, such as an air/fuel mixture, enters the venturi interior 960 through the tangential apertures 958 to create turbulence, and flows generally helically through the venturi 954.

Figures 20 and 21 show another embodiment of the invention, particularly for applications in the field of inhaler type medicaments. The present embodiment illustrates a fluid vaporization system 1120 that generally comprises: a compressible reservoir 1122, a source of compressed gas 1124, a venturi 1126, a plurality of vortex chamber housings 1228, 1244, 1248, 1250, 1252, 1254, 1256, 1258, and a system outlet 1128. Generally, by delivering compressed gas into system 1120, fluid 1130 is drawn from compressible container 1122 and flows through conduits 1132 and 1134 (located in base 1136) into venturi 1126 (also located in base 1136). In the venturi 1126, the fluid 1130 mixes with the compressed gas and exits the venturi 1126 through the venturi outlet 1238 as suspended particles. The fluid is then passed through a series of vortex chamber housings to break up the fluid into smaller droplets and further vaporize the unvaporized or partially vaporized droplets in the fluid. Finally, the fluid is discharged from the system through system outlet 1128.

Specifically, as shown in FIG. 21, the compressible container 1122 includes a bag having flexible side walls 1140 and a flexible bottom 1142. The flexible wall 1140 and the flexible bottom 1142 enclose a hollow interior 1144 in the compressible container 1122. When the compressible container 1122 is compressed, the volume 1144 of the hollow interior decreases, which increases the pressure in the hollow interior 1144.

The compressible fluid container outlet 1160 is bounded by the inner surface 1161 of the connector 1148. Preferably, the connector 1148 is made of a pliable material, such as rubber. Connector 1148 is coupled to base 1136 via barbed connector 1150. Barbed connector 1150, as shown, includes a threaded portion 1152, a shoulder 1154, and a barbed extension 1156. Barbs 1158 are formed on the extensions 1156 to allow a resistance or interference fit to be created between the barbed connector 1150 and the container connector 1148. The barbed connector 1150 further includes a channel 1159 that extends from the outlet 1160 to the conduit 1132, allowing the fluid 1130 in the hollow interior 1144 of the compressible container 1122 to pass from the container 1122 into the conduit 1132. Thus, in the assembled configuration of FIGS. 20 and 21, threaded portion 1152 of connector 1150 is threadably coupled to base 1135. The compressible container 1122 can be secured or removed by pressing the flexible connector 1148 over the extension 1156 with a resistive or interference fit with the barbed connector 1150. In this manner, a tight, resistive interference fit is created between barbed extension 1156 and inner surface 1161 of fitting 1148.

The compressible container 1122 is shown housed in a pressure chamber 1164, the pressure chamber 1164 being bounded by an inner surface 1166 of a pressure housing 1168. The pressure housing 1168 is secured to the base 1136 by threads 1170 at one end thereof to threadably couple the pressure housing 1168 to the base 1136. To create a complete gas seal between base 1136 and housing 1168, a gasket, such as O-ring 1172, is installed and preferably compressed between boss 1174 of housing 1168 and contact surface 1176 of base 1136.

Pressure chamber 1164 is pressurized by receiving gas from compressed gas source 1124 via compressed gas conduit 1178. Preferably, the source of compressed gas may be connected to any suitable device, such as a pump or a compressed gas tank. Also, the compressed gas may include air, oxygen, nitrous oxide, or any other suitable gas.

A compressed gas conduit 1178 is shown located in base 1136 and extends from venturi inlet 1180 to pressure chamber 1164. Pressurized gas is supplied to pressure chamber 1164 through conduit 1178 to increase the pressure of pressure chamber 1164. The increase in pressure chamber pressure causes compressible reservoir 1122 to compress, thereby forcing fluid 1130 out of reservoir 1122 through outlet 1160 and connector channel 1159.

As shown in fig. 21, compressible reservoir 1122 may contain a liquid fluid 1130 and, in some cases, a quantity of a gaseous fluid, such as air 1182. The system 1120 can be used to vaporize a wide variety of fluids. In one embodiment, the liquid fluid to be vaporized comprises a drug that can be received by the patient by inhalation. Preferably, only a small portion of the unvaporized fluid has a droplet size greater than 5 microns as the fluid exits the system through system outlet 1128. The fluid medicant is vaporized as it passes through the system 1120 so that the fluid medicant can be effectively inhaled by the patient.

A flow regulator or ball valve assembly 1184 is connected to the fluid conduit 1132 extending from the outlet 1160. The flow regulator 1184 is shown generally as including a regulator housing 1186, a ball 1188 positioned within a suitably sized cavity, a set screw 1190, and a biasing member 1192. The flow regulator housing 1186 is removably secured to the base 1136 by a threaded connection. As shown, ball 1188 is positioned in a spherical opening 1194 in base 1136. The ball 1188 is held within the spherical opening 1194 by a biasing element 1192. as shown in FIG. 21, the biasing element 1192 may comprise a conventional coil spring. In this configuration, as the pressure in the hollow interior 1144 of the compressible container 1122 increases, the pressure in the conduit 1132 increases accordingly, which overcomes the bias and pushes the ball 1188 away from the spherical opening 1194, allowing fluid to flow from the conduit 1132 to the conduit 1134 bypassing the ball 1188.

The amount of pressure required to remove the ball 1188 from the spherical opening 1194 may be adjusted by adjusting the compression of the biasing element 1192. The compression, and therefore the force generated by the biasing element 1192, may be adjusted by screwing or unscrewing the adjustment screw 1190 relative to the housing 1186. The more the screw is advanced toward the housing 1186, the greater the compression of the biasing element 1192. Thus, the greater the pressure required to move the ball 1188 to allow fluid to flow through the regulator 1184. Conversely, as the screw 1190 is withdrawn from the housing 1186, the compression of the biasing element 1192 is reduced, and thus the less pressure in the conduit 1132 is required to move the ball 1188 away.

Ball valve assembly 1184 is but one of many regulators that may be effectively used to control the flow of fluid between conduits 1132 and 1134. It should be appreciated that any suitable valve or other flow regulating device may be effectively utilized.

In addition to supplying compressed gas to compressed gas conduit 1178, compressed gas source 1124 also provides compressed gas to venturi 1126 via venturi inlet 1180. The venturi 1126 generally includes a venturi inlet 1180, a venturi outlet 1196, and a narrow throat 1198. A narrow throat 1198 is shown between the venturi inlet 1180 and the venturi outlet 1196.

The narrow throat 1198 significantly increases the velocity of the compressed gas as the compressed gas flow F passes from the compressed gas source 1124 through the venturi 1126. The high velocity gas passing through the venturi throat 1198 creates a low pressure zone at the venturi throat 1198. As shown, the narrow throat 1198 is in fluid communication with the conduit 1134. The low pressure zone at the narrow throat 1198 helps to draw fluid from the conduit 1134 into the high velocity, low pressure gas stream through the venturi narrow throat 1198. As fluid 1130 enters narrow throat 1198 through conduit 1134, fluid 1130 mixes with compressed gas from compressed gas source 1124. Due to the pressure differential created by the high velocity gas passing through the narrow throat 1198 of the venturi and the venturi 1126, the fluid 1130 advantageously exits the venturi 1126 through the venturi outlet 1196 in a suspended particulate form.

After exiting venturi 1126, the fluid enters mixing chamber 1200 through a plurality of apertures 1202 in hollow passageway 1204. As shown in fig. 21, the passageway 1204 is integral with the base 1136 and includes a hollow interior 1206 in fluid communication with the venturi outlet 1196. Thus, upon exiting the venturi 1126 through the venturi outlet 1196, the fluid enters the mixing chamber 1200 through the aperture 1202 of the passageway 1204.

The mixing chamber 1200 is enclosed by the outer surface 1210 of the base, the inner surface 1212 of the tube 1214, and the outer surface 1216 of the vortex chamber housing 1228. The vortex chamber housing 1228 is identical in structure and function to the vortex chamber housing 940 described above and shown in figure 17.

As shown in fig. 21, the swirl chamber housing 1228 also includes a bottom exterior surface 1220 that is adjacent to and abuts the passage 1204 to allow fluid passing through the passage hollow interior 1206 to exit the hollow interior through the orifice 1202. After the fluid flow F enters the mixing chamber 1200, the fluid then enters the vortex chamber 1224 through the tangential slots 1222 of the vortex chamber housing 1228. The tangential slots 1222 are identical to the elongated tangential slots 950 shown in fig. 17 and described above. The tangential slots 1222 provide tangential entry of fluid into the vortex chamber 1224. Because the slots 1222 are oriented tangentially, the fluid enters the vortex chamber 1224 tangentially, creating a vortex in the vortex chamber 1224.

An outlet element 1230 is connected to the vortex chamber housing 1228 to deliver fluid from the vortex chamber 1224 to the mixing chamber 1232. The outlet element 1230 is shown as being mounted to the vortex chamber housing 1228 by an interference fit, but may be secured to the vortex chamber housing by a variety of conventional means.

The outlet member 1230, as shown in fig. 21, includes a body 1234 having an annular groove 1236 around the periphery of the body 1234. Grooves 1236 may contain a gasket, such as O-ring 1238, to prevent fluid from flowing directly from mixing chamber 1200 to mixing chamber 1232 without passing through swirl chamber 1224. The outlet element 1230 also includes a hollow interior 1240 and an orifice 1242 for directing fluid from the swirl chamber 1224 through the outlet element 1230 into the mixing chamber 1232.

Upon exiting the outlet element 1230 through the orifice 1242, the fluid passes through the mixing chamber 1232 and the vortex chamber housing 1244 in the same manner as through the vortex chamber housing 1228. Similarly, fluid exits the vortex chamber housing 1244 through an outlet element 1246, which is of the same construction as the outlet element 1230 shown in figure 21. In the same manner, as shown in fig. 20, fluid passes through swirl chambers 1248, 1250, 1252, 1254, 1256 and 1258 and correspondingly through outlet elements 1260, 1262, 1266, 1268 and 1270. As illustrated, the vortex chamber housings 1244, 1248, 1250, 1252, 1254, 1256, and 1258 are identical in structure and function to the vortex chamber housing 1228. Similarly, the outlet elements 1246, 1260, 1262, 1264, 1266, 1268, and 1270 are identical in structure and function to the outlet element 1230 shown in FIG. 21. Therefore, further description of these features is not necessary.

The fluid exits outlet element 1270 (fig. 20) and enters discharge chamber 1272, which is bounded by outlet element 1270 and inner surface 1274 of outlet housing 1276. As shown, the outlet housing 1276 is fixedly secured to the tube 1214. The inner surface of the outlet housing 1276 is shown attached to the tube 1214 by an interference fit, and the outlet housing 1276, also referred to as the exhaust housing 1276, may also be secured to the tube 1214 by a variety of methods, including bonding or threaded attachment methods.

The exhaust housing 1276 also includes a plurality of outlet passages 1278 for discharging fluid from the exhaust chamber 1272 to the exhaust port 1280. The drain hole 1280 also includes a threaded portion 1282 that allows a conventional threaded connector, such as a hose connector 1284, to be threaded onto the drain housing 1276 to receive fluid discharged from the drain hole 1280. The distal end 1285 of the conventional connector 1284 may be attached in a conventional manner to a variety of fluid receiving devices, such as a suction nozzle, or other structure for receiving a fully vaporized stream of the fluid 1130.

The operation of the embodiment shown in fig. 1-6 is described below. Liquid, such as fuel, is electronically controlled, metered, and injected through the outlet 46 of the fuel injector 38 to suspend particulates into the premixing chamber 44. Although the fluid is a fuel, other fluids, such as pharmaceuticals and waste fluids, may be vaporized and homogenized using the apparatus and method described above.

As fuel is injected into the pre-mix chamber 44, the throttle plate 84 opens to allow a quantity of air to enter the venturi 82. The amount of air allowed to pass through the throttle plate 84 is proportional to the amount of fluid injected into the premix chamber by the outlet 46 of the fuel injector 38. The vacuum created by the engine draws fluid from the mixing chamber 44 through an aperture 66 in the chamber housing 54.

When the engine is operating, a partial vacuum is created in the engine intake (not shown). With the throttle plate in the closed position, the low pressure air/fuel mixture in the pre-mix chamber 44 is drawn tangentially into the swirl chamber 64 through the orifice 66. Specifically, air entering the swirl chamber enters the ambient air conduit 50 through the slot 94, the ambient air passage 100 and the conduit 102. Ambient air enters the pre-mix chamber from the ambient air duct 50 where it mixes with the atomized fuel before entering the bore 66 as an air/fuel mixture.

The air/fuel mixture enters the vortex chamber 64 generally tangentially, and due to the fluid from the orifices 66, the fluid rotationally accelerates within the vortex chamber 64. The amount of fluid entering each of the apertures 66 is substantially equal due to the presence of the sleeve 60. Depending on the position of the orifice relative to the outlet 70, the inner surface 56 of the sleeve restricts the flow of fluid into the orifice. The outlet 70 comprises a low pressure end of the fluid passing through the swirl chamber 64. In essence, the sleeve creates increased restriction to the holes near the outlet 70 and less restriction, if any, to the holes furthest from the low pressure end (outlet 70).

Once the fluid enters the vortex chamber 64, the fluid is rotationally accelerated, causing any unvaporized droplets in the fluid to break up into smaller droplets, or to vaporize, or both. When the fluid reaches the outlet 70, the fluid enters the intermediate chamber 136 from the chamber 64 as a rotating column of fluid. In the intermediate chamber 136, the fluid collapses on itself, thereby disrupting the rotating column of fluid and creating additional turbulence and homogenization of the fluid.

The partial vacuum of fluid produced by the engine intake is then drawn through the elongated orifice 106 of the venturi 82. The elongated holes 106 are larger and more numerous than conventional small circular venturi chamber holes because they are designed to reduce any pressure drop and achieve flow rates as high as 60 CFM. In venturi 82, ambient air introduced by throttle plate 84 mixes with the air/fuel mixture as it enters through orifice 106. The ambient air/fuel mixture is further mixed and at least partially homogenized in the venturi 82.

As fluid enters the intake chamber 146, the partial vacuum created by the engine intake draws the fluid through the centrifugal inlet 144. The inlet chamber provides further mixing and homogenization of the fluid and directs the fluid tangentially into the centrifugal chamber 152. Specifically, the baffle 150 located in the inlet chamber 146 creates a series of tangential passageways 200, 202 and 204 through which the partial vacuum of the engine intake pipe causes fluid to enter the centrifugal chamber 152 in a tangential direction.

The fluid is rotationally accelerated in chamber 152 causing the largest or heaviest droplets to move by their own weight toward the periphery of chamber 152 where they collide with inner surface 156 and further break up and vaporize.

To reduce the volume of the centrifugal chamber 152, the height of the sidewall 156 is preferably less than the inner diameter 114 of the venturi 82 at the venturi outlet 110. Additionally, to decrease the volume of the centrifugal chamber 152 and increase centrifugal flow in the chamber 152, an extension member 162 extends from the centrifugal housing top wall 160.

Fluid is then drawn into the four outlets 154 by the vacuum of the engine. As the lighter droplets in the fluid centrifugally progress toward the center of the chamber 152, they are directed at an angle from the conical portion of the top surface 170 of the chamber profile into the holes 182 of the conical portion 180 and into the four outlets 154. By discharging fluid from the chamber in the above-described manner, a more even distribution of hydrocarbons is obtained, since the hydrocarbons are generally directed towards the outside of the centrifugal flow of the chamber. In contrast, when only one outlet is used, the centrifugal discharge is not uniform because the hydrocarbons are directed to the outside of the centrifugal flow.

Referring now to the embodiment of the invention illustrated in FIG. 7, the swirl structure 220 has atomized fuel provided by fuel injector 222. The fuel injectors 222 inject fuel into the premix chamber 242. Ambient air also enters the pre-mix chamber 242 through an ambient air conduit 244. In the premix chamber, the atomized fuel and ambient air mix and enter the swirl chamber 248 as an air/fuel mixture through the orifice 260.

In a similar manner to the sleeve 60 (FIG. 1), the sleeve 272 acts as a source of differential pressure to regulate the flow through each of the apertures 260. The air/fuel mixture enters the swirl chamber 248 through the orifices 260 in a manner similar to that described for the swirl chamber 54 and the orifices 66 in fig. 1. As the air/fuel mixture exits the U-shaped outlet 340, it enters the mixing chamber 350 before entering the swirl chamber 250 through the orifice 262. In this configuration, the bore 262 receives the air/fuel mixture from the outlet of the swirl chamber 248 to maintain a substantially constant air/fuel ratio as the air/fuel mixture passes through the chambers 248 and 250.

The air/fuel mixture then exits the U-shaped outlet 342 and enters the mixing chamber 352 before entering the vortex chamber 252 through the orifice 264. Also, as the fluid passes through the swirl chambers 250 and 252, the air/fuel mixture maintains a substantially constant air/fuel ratio.

After exiting the outlet 344 of the chamber housing 228, the fluid continues through the mixing chamber 354, the orifice 266, and the swirl chamber 254 in exactly the same manner as described with respect to the swirl chamber 252. After exiting the U-shaped outlet 346, the fluid enters the mixing chamber 356, enters the final chamber 256 through the aperture 268, and exits through the outlet 348.

Through the 5 chambers 248-256, the fluid is constantly vaporized and converted to the gas phase as it passes from one chamber to the next. The present embodiment therefore maintains a substantially constant air/fuel ratio of the air/fuel mixture as it passes through the several chambers.

Figure 17 shows another embodiment of a vortex chamber housing. In operation, the vortex chamber housing 940 receives fluid from the tangential slots 950 into the chamber interior 952 to create a swirling flow of fluid in the chamber interior 952. The elongated slot 950 introduces fluid tangentially into the chamber interior as a layer of fluid along the vortex chamber housing inner surface 946 to prevent the accumulation of droplets on the inner surface 946. As the fluid swirls in the chamber 952, the pressure differential and the overall turbulence of the swirling flow in the chamber 952 causes the fluid to be vaporized and homogenized.

Fig. 18 and 19 illustrate an alternative embodiment of a venturi 954 formed in accordance with the principles of the present invention. In operation, venturi 954 receives a flow of fluid from venturi inlet 962. The fluid flow is then mixed with an air/fuel mixture which enters the venturi interior 960 through tangential apertures 958 in the wall 956 to create a helical flow through the venturi 954. The tangential introduction of the air/fuel mixture into the venturi interior 960 causes the vortex flow through the venturi 954 to swirl into a helical shape. The air/fuel mixture is preferably introduced into a narrow throat 959 inside the venturi 960 because the narrow throat 959 includes a region where air flows fastest in the venturi 954. By creating a helical flow of fluid in the venturi 954, turbulence is significantly enhanced, as well as vaporization and homogenization.

As mentioned above, fig. 20 and 21 show another embodiment of the present invention. In this embodiment, positive pressure is provided to the system 1120 by a positive pressure source 1124. The positive pressure source delivers gas under pressure to the venturi inlet 180 and the compressed gas conduit 1178. Compressed gas enters the pressure chamber 1164 through a compressed gas conduit 1178. As the pressure in the pressure chamber 1164 increases under the influence of the compressed air, the compressible container 1122 is compressed, thereby decreasing the volume and increasing the pressure of the container hollow interior 1144. When compressible reservoir 1122 compresses, fluid 1130 in reservoir 1122 is forced out of reservoir 1122 and into fluid conduit 1132 through outlet 1160, channel 1159.

The flow of fluid from fluid conduit 1132 into conduit 1134 may be controlled by regulator 1184. In the biased position shown in fig. 21, the ball 1188 is biased against the ball seat 1194 to prevent fluid flow from the conduit 1132 to the conduit 1134. However, as the pressure in the conduit 1132 increases, overcoming the bias towards the ball seat 1194, the ball 1188 is withdrawn from the ball seat, allowing fluid to flow through the conduit 1132 to the conduit 1134.

The bias of the ball 1188 toward the ball seat 1194 may be adjusted by threading the screw 1190 into and out of the housing 1186. As the screw 1190 is threaded into the housing 1186, the spring 1192 compresses, thereby increasing the bias on the ball 1188. Conversely, when the screw 1190 is unscrewed from the housing 1186, the spring 1192 relaxes, thereby reducing the amount of bias on the ball 1188. When the bias on the ball 1188 is reduced, less pressure in the conduit 1132 may dislodge the ball 1188 and allow fluid to flow from the conduit 1132 into the conduit 1134.

After flowing through the regulator 1184, the fluid passes through the conduit 1134 and enters the venturi throat 1198 in a suspended particulate form. As the compressed gas passes through the venturi 1126, the velocity increases as the gas passes through the narrow throat 1198, thereby creating a low pressure region at the narrow throat 1198. The low pressure created by the high velocity of the gas flowing through the narrow throat 1198 of the venturi helps draw the fluid through the conduit 1134 into the narrow throat 1198.

In venturi throat 1198, compressed gas from compressed gas source 1124 is mixed with fluid 1130. After mixing with the compressed gas, the fluid exits the venturi 1126 as a mist through the venturi outlet 1196 in suspended particulate form. Fluid enters the mixing chamber 1200 from the venturi outlet 1196 through the aperture 1202 of the passage 1204. Fluid from the mixing chamber 1200 enters the vortex chamber 1224 through the tangential slots 1222 creating a vortex in the vortex chamber 1224 breaking any unevaporated droplets in the vortex into smaller droplets and vaporizing.

Fluid then flows from the swirl chamber 1224 into the mixing chamber 1232 through the orifice 1242 in the outlet element 1230. The fluid continues through subsequent vortex chamber housings 1244, 1248, 1250, 1254, 1256, 1258 and through subsequent outlet elements 1246, 1260, 1262, 1264, 1266, 1268 and 1270 in the same manner as through the vortex chamber housing 1228 and outlet element 1230, respectively. Through each subsequent vortex chamber housing, the fluid is further homogenized and vaporized.

After exiting the final outlet element 1270, the fluid enters the passage 1278 through the outlet chamber 1272, thereby providing fully vaporized fluid to the outlet port 1280. To deliver the vaporized fluid to its final destination, the fluid may be passed through a conventional hose connector 1284.

Figure 22 shows another embodiment of the present invention directed to vaporizing and aerosolizing a liquid for inhalation by a patient. Conceptually, the system 1300 of the present embodiment includes multiple stages of vortex chambers 1302 and 1308, each having different characteristics. In this embodiment, the orifices 1310 of the first stage vortex chamber 1302 are arranged in parallel rows and columns. In the second and third stages, the orifices 1312 of the vortex chambers 1304 and 1306 are staggered, similar to the orifices 66 of the vortex chamber 64 shown in fig. 3. In the last stage, the swirl chamber 1308 has grooves 1314, analogous to the tangential grooves 950 shown in FIG. 17.

For the embodiment 1300 in figure 22, the orifices 1312 of the second and third stage vortex chambers 1304 and 1306 are smaller than the orifices 1310 of the first stage vortex chamber 1302. However, the total surface area of the holes 1312 in the second and third stages is equal to the total surface area of the holes 1310 of the first stage. This is because the second and third stage vortex chambers 1304 and 1306 have more orifices. In other words, although the holes 1312 are small, the number of the holes 1312 is large.

In this embodiment, compressed gas or air, typically at 125psi, is introduced into the system 1300, where a positive pressure 1318 is created. Fluid is drawn in through the holes 1320. The fluid comprises a medicament to be aerosolized/vaporized and may include an inert carrier, such as saline. The side port 1316 directs fluid out of the vortex chamber 1302 and into it through the orifice 1310. This process is repeated in each stage (not shown).

This embodiment may have a variety of variations including more or less stages, and combinations of different swirl chambers with different orifice patterns 1310, 1312 and slots 1314. Another structural variation is to create a large pressure drop in the first stage and a small pressure drop in each of the remaining stages, bringing the final outlet 1322 to a pressure close to atmospheric pressure. This can improve the processing efficiency.

Another variation of all embodiments is to include a heating process. Either the input air 1318 or the external surfaces of the system are heated to provide heat to the air or fluid as it passes through each stage of the device. For example, when used for fluid isolation, such as desalination, the heating system can produce better results depending on other factors including pressure and number of vortex chambers. This fluid segregation capability, at least in the embodiment 1300 of fig. 22, is believed to be a kinetic evaporation process. The present invention may include one or more vortex chambers 1302 and 1308 that may be easily removed for cleaning and deposit removal. Alternatively, the entire system may be soaked or flushed back and forth with fluid to clean the device.

Another embodiment of the invention is shown in fig. 23. The system 1330 of this embodiment includes a single stage vortex chamber 1340 having a first portion 1341 of reduced pressure and a second portion 1343 of reduced velocity. Compressed air 1318 enters through an inlet nozzle 1332. A tapered venturi stage 1334 is then created by defining the diameter 1336 of the flow as 6.350mm (0.250 inch). Followed by an enlarged venturi stage 1338 having a diameter of about 9.398mm (0.370 inch). Fluid enters this enlarged venturi stage 1338 through a fluid inlet 1320, the inlet 1320 being approximately 1.5875mm (0.0625 inch) in diameter.

The air/fluid mixture then flows out of the first portion 1341 and to the vortex chamber 1340. In this embodiment, the swirl chamber 1340 includes staggered holes 1312. Specifically, the vortex chamber 1340 has 40 holes with a diameter of about 0.889mm (0.035 inch), thereby forming a total surface area of about 24.8387mm²(0.0385 square inches).

The air/fluid mixture exits the vortex chamber 1340 through a tapered venturi 1342. This tapered venturi 1342 has a venturi opening 1344 with a diameter of about 2.5273mm (0.0995 inches).

The vortex chamber 1340 is located between two annular gaskets 1354 and 1354', which securely hold the vortex chamber in the system 1330 and direct the air/fluid through each section. The vortex chamber 1340 and an annular washer 1354 slide in the inner wall 1346 of the deceleration second portion 1343, as indicated by arrow 1350. When in place, they are close to each other and held in place by the dividing wall 1348, and the vortex chamber 1340 is located inside the deceleration second portion 1343.

The deceleration second section 1343 includes a deceleration chamber 1352. As the air/fluid exits the swirl chamber 1340 through the tapered venturi 1342, a conical swirling flow is created. The outlet 1322 at the end of the deceleration chamber 1352 is an atomized or vaporized air/fluid mixture of very fine particles at a pressure close to atmospheric pressure.

In this embodiment, the overall length of system 1330 is approximately 147.3mm (5.8 inches). The reduced pressure first portion 1341 is about 32.385mm (1.275 inches) and the reduced velocity second portion 1343 is about 116.8(4.6 inches) long. The vortex chamber 1340 and annular gasket 1354, when located in the deceleration second portion 1343, extend about 40.6mm (1.6 inches) in the deceleration second portion 1343. Deceleration chamber 1352 is approximately 76mm (3 inches) long. The inner diameter of the deceleration second portion 1343 is about 34.925(1.375 inches).

The test results for this example were obtained using saline as the working fluid. Compressed air 1318 at 185psi (18 cubic feet per minute) is input through inlet nozzle 1332. The pressure drop is created by the first and second tapered venturi stages 1334, 1342 as compared to ambient atmospheric pressure. The pressure drop created when the fluid exits the vortex chamber 1340 into the deceleration chamber 1352 is 185 psi. As a result, the amount of liquid treated by the system increased to 3ml per minute. Deceleration chamber 1352 may also act as a separator for large droplets when very fine droplets intermix with large droplets (e.g., when atomizing certain liquids). Deceleration chamber 1352 is particularly effective in separating these large droplets. As the fluid exits the vortex chamber 1340, a conical swirling flow is created. The large droplets form a thin layer (when saline is used) immediately before the venturi outlet 1344. Very fine particles are discharged at the end of the chamber.

When the embodiment of fig. 23 and 24 is used for fluid segregation, the operation includes a pneumatic/dynamic evaporation process. A single stage vortex chamber and venturi or nozzle produce vortex-related shear forces on the fluid that can reduce droplet size and enhance separation.

Another embodiment of the present invention is directed to vaporizing and aerosolizing a liquid for inhalation by a patient, as shown in figure 24. This embodiment 1360 is similar to the embodiment 1330 of FIG. 23, including a single stage vortex processor (chamber) 1364, a tapered nozzle 1368 and a velocity reduction chamber 1374. Embodiment 1360 includes an air-gas input mixer portion 1362, shown in detail in FIGS. 25A-C. The gas/fluid mixture flows through opening 1363, which has a radius of about 15.875mm (0.625 inches). The gas/fluid mixture flows to a vortex processor 1364, shown in detail in fig. 26A-C. The vortex processor 1364 has a single row of holes 1366 that open tangentially into the central chamber 1367. The hole diameter was about 1.397mm (0.055 inch). The inside diameter of the chamber wall of the vortex processor 1364 is about 2.134mm (0.084 inch). The outer diameter 1361 of the vortex processor 1364 is about 25mm (1 inch) and the inner diameter 1369 is about 15.8750mm (0.6250 inches) and has a central delivery hole 1365 with a diameter of about 1.1684mm (0.0460 inches). Of course, all dimensions and openings may be varied to enhance the preferred performance of the invention.

As the air/fluid mixture passes through vortex processor 1364, it enters a venturi chamber 1370 defined by nozzles 1368. The exterior of nozzle 1368 tapers to an end having a constant inner diameter 1372 of about 2.5273mm (0.0995 inches). The air/fluid mixture is discharged into the deceleration chamber 1374 and then out the end of the deceleration chamber 1374 at a pressure near ambient atmospheric pressure, as indicated by arrow 1322. The parts are joined together using a gasket or O-ring 1376 to provide a fluid tight seal.

In this embodiment, the deceleration chamber 1374 is approximately 76mm (3 inches) long and has an inner diameter of approximately 28.9941mm (1.1415 inches). Nozzle 1368 is approximately 25mm (1 inch) long and extends into deceleration chamber 1374. Nozzle 1368 defines a venturi chamber 1370 having a conical inner wall with a radius of about 6.35mm (0.25 inches). Figures 27A and B illustrate a different nozzle 1368 in which an embodiment of the nozzle defines a venturi chamber 1370 having inner walls forming an angle of about 60 degrees (as indicated by arrow 1378) and decreasing in size to an opening having an inner diameter of about 2.5273mm (0.0995 inches). The length of the nozzle 1368 may vary depending on the desired atomization, vaporization, or segregation properties, such as a short nozzle in fig. 27A or a long nozzle in fig. 27B of about 25mm (1 inch) in length.

The above system and method are also applicable and useful for the decomposition, vaporization and homogenization of waste streams in incineration and waste management. When the waste liquid droplets are broken down to their very small size, the waste liquid entering the incinerator will burn more efficiently, thereby minimizing pollution and increasing the efficiency of incineration of the waste liquid.

Although the present invention has been illustrated and described with reference to the illustrated embodiments, it is well within the spirit and scope of the present invention to make various changes, omissions and additions in the form and detail thereof.

Claims (17)

1. A vortex system for atomizing an inhalation liquid, comprising:

a venturi element in fluid communication with a source of compressed gas and also in fluid communication with said source of fluid;

a vortex element comprising:

a chamber housing enclosing a vortex chamber, in fluid communication with the venturi element, for generating a rotational flow in the vortex chamber and atomizing the liquid;

a plurality of apertures in the chamber housing to enable fluid to be input tangentially into the vortex chamber to create a rotational flow in the vortex chamber;

a chamber outlet in fluid communication with the vortex chamber to allow fluid to be expelled from the vortex chamber.

2. The vortex system according to claim 1 wherein said plurality of apertures are arranged in rows and columns in said chamber housing.

3. The vortex system according to claim 2, further comprising:

a second eddy current element comprising:

a second chamber housing enclosing a second vortex chamber in fluid communication with the chamber outlet;

a plurality of orifices in said second chamber housing for tangentially inputting fluid into said second vortex chamber to create a swirling flow in said vortex chamber, said plurality of orifices being arranged in rows and staggered columns in said second chamber;

a second chamber outlet in fluid communication with the second vortex chamber to cause fluid to be expelled from the second vortex chamber.

4. The vortex system according to claim 3, further comprising:

a third vortex element identical to the second vortex element, wherein a third chamber housing enclosing a third vortex chamber is in fluid communication with the second chamber outlet.

5. The vortex system according to claim 4, further comprising:

a fourth vortex element comprising:

a fourth chamber housing enclosing a fourth vortex chamber in fluid communication with a chamber outlet of the third chamber housing;

a series of tangentially elongated slots in said fourth chamber housing tangentially inputting fluid into said fourth vortex chamber to create a swirling flow through the vortex chamber, wherein each tangential slot extends from the top to the bottom of said fourth vortex chamber.

6. A centrifugal vortex system according to claim 1 wherein the chamber housing has an inner chamber wall, the inner chamber wall comprising a textured surface formed on the inner chamber wall.

7. A centrifugal vortex system according to claim 1 wherein the chamber housing has an inner chamber wall comprising a plurality of steps formed in the inner chamber wall.

8. A centrifugal vortex system according to claim 1, comprising: a plurality of said vortex elements in fluid communication in series, wherein the chamber housing of a first element of said plurality of vortex elements is in fluid communication with said venturi element.

9. A vortex system for atomizing an inhalation liquid, comprising:

an eddy current element comprising:

a chamber housing enclosing a vortex chamber in fluid communication with a source of compressed gas and with the source of liquid, creating a vortex in the vortex chamber and atomizing the liquid;

a plurality of apertures in the chamber housing to enable fluid to be input tangentially into the vortex chamber to create a rotational flow in the vortex chamber;

a chamber outlet in fluid communication with the vortex chamber to allow fluid to exit the vortex chamber; and

a deceleration element in fluid communication with the chamber outlet.

10. The vortex system according to claim 9 further comprising:

a venturi element in fluid communication with a source of pressurized gas, and also in fluid communication with said source of fluid, and with said chamber housing.

11. The vortex system of claim 9 wherein said chamber outlet includes a fluid pressure reduction element, said pressure reduction element being in fluid communication with said vortex chamber and said deceleration element.

12. The vortex system of claim 11 wherein said fluid pressure reduction element comprises a venturi.

13. The vortex system of claim 11 wherein said fluid pressure reduction element comprises a nozzle.

14. The vortex system of claim 9 wherein said decelerating element comprises a chamber.

15. The vortex system of claim 9 wherein said apertures are arranged in rows and staggered columns in said chamber housing.

16. The vortex system of claim 9 wherein said apertures are aligned in said chamber housing.

17. A method of atomizing or vaporizing a fluid comprising:

receiving a compressed gas;

drawing in a fluid and mixing said fluid with said compressed gas using a venturi element charged with said compressed gas;

creating a swirling flow in a vortex that atomizes the mixture of fluid and compressed gas;

further mixing the mixed liquid and gas in the vortex, wherein the mixed fluid and gas enters the vortex through a plurality of tangential holes located in a chamber wall surrounding the vortex;

reducing the pressure of the mixed fluid and gas flowing from the vortex using a nozzle element;

the mixed liquid and gas are decelerated in a chamber element.