IMPROVED FCC FEED INJECTOR FAN TIP DESIGN

Abstract: The invention relates to fluidized catalytic cracking ("FCC") processes using a high fluid throughput and low pressure drop, liquid atomizing process and apparatus. The process comprises forming a fluid mixture of a hot feed oil and a dispersion gas, such as steam, atomizing the mixture to form droplets, and then distributing the droplets into the FCC process. The apparatus (180) comprises a nozzle (184) having an improved spray distributor (150) end section.

Description: IMPRONED FCC FEED INJECTOR FAN TIP DESIGN This application is a continuation in part of U.S. Patent Application Serial Number 09/271.813. filed March 18. 1999. BACKGROUND OF THE DISCLOSURE FIELD OF THE INVENTION The invention relates to fluidized catalytic cracking ("FCC") processes using a high fluid throughput and low pressure drop, liquid atomizing process and apparatus. The process comprises forming a fluid mixture of a hot feed oil and a dispersion gas. such as steam, atomizing the mixture to form droplets, and then distributing the droplets into the FCC process. The apparatus comprises a nozzle having an improved spray distributor end section. BACKGROUND OF THE INVENTION Fluid atomization is well known and used in a wide variety of applications and processes. These include, for example, aerosol sprays, the application of pesticides and coatings, spray drying, humidification. mixing, air conditioning, and chemical and petroleum refinery processes. For most applications, a fluid under pressure, with or without the presence of an atomizing agent, is forced through an atomization nozzle having a relatively small orifice. Atomization occurs at the downstream side of the orifice, with the degree of atomization determined by the orifice size, the pressure drop across the orifice, fluid density, viscosity, and surface tension, etc.. as is known. Atomization is increased and the droplet size is decreased, with decreasing orifice size and increasing pressure drop. Increasing the degree of atomization of relatively viscous fluids at high flow rates, such as the heavy petroleum oil feeds used in an FCC process, or fluid cat cracking as it is also called, is particularly challenging. FCC is an established and widely used process in ihe petroleum refining industry, primarily for converting high boiling petroleum oils to more valuable lower boiling products, including gasoline and middle distillates such as kerosene, jet and diesel fuel, and heating oil. In an FCC process, a preheated feed, often mixed with an atomization promoting fluid, such as steam, is atomized and brought into contact with a particulate. hot cracking catalyst flowing up through a riser which comprises the catalytic cracking reaction zone. Smaller oil feed droplet sizes in the reaction zone result in more feed conversion to valuable products, particularly with the incorporation of heavy feed material, such as a resid. in the FCC feed. Oil that doesn ' t make contact with the uprising catalyst particles, thermally cracks primarily to light gases, such as methane, and coke. As a consequence, efforts continue to try to find economically viable means to decrease the droplet size of the atomized oil. and preferably without either (i) an unacceptable' high pressure drop through the-atomizer or nozzle or (ii) increasing the amount of steam or other atomization promoting agent. Examples of such efforts are disclosed in. for example. US 5.289.976 and US 5.173.175 which produce an average feed droplet size in the range of about 400- 1000 microns. There is still a need for finer atomization of the heavy oil feed for the FCC process and of other fluids for other processes as well. It would be particularly beneficial if the droplet size of the atomized liquid could be reduced to less than 300 microns. SUMMARY OF THE INVENTION The invention relates to a process and apparatus for atomizing a liquid. The process and apparatus are useful for atomizing and injecting hot feed oil into a reaction zone of a fluid cat cracker, to achieve a relatively small drop size, and uniform drop size distribution of the atomized oil drops or droplets. More particularly, the apparatus of the invention relates to a spray distributing means, such as an expanding fan-shaped spray distributor, the interior of which comprises a fan-shaped cavity open at its upstream and downstream ends, preferably adjacent the downstream side of the atomizing orifice, for controlling the shape of the atomized spray. In another embodiment, the invention comprises a process for atomizing a liquid into a spray of liquid drops, and then conducting the drops through spray distributing means in order to form a distributed spray of droplets. In a preferred embodiment, the apparatus of the invention briefly comprises a body containing a cavity within, comprising an impingement mixing zone and a shear mixing zone downstream of the impingement mixing zone, wherein the cavity is elongated in the direction of fluid flow and extends through the body. Preferably the body contains a means for splitting a fluid stream adjacent the upstream end of the body into two separate streams, with an orifice entrance for each stream to enter the cavity and into the impingement mixing zone. The apparatus may also include a spray distributing means adjacent to its downstream end. the fluid entrance of which is adjacent the fluid exit of the shear mixing zone, with which it is in fluid communication. Preferably, the spray distributor means is a spray distributor. The preferred spray distributor is a three dimensional member having ( 1) a front surface separated from a rear surface by a length L along a first axis and (2) a continuous, internal, fan-shaped channel open at the front and rear surface, the channel having (a) flat, parallel top and bottom surfaces separated by a constant height h measured parallel to a second axis perpendicular to the first axis and (b) curved first and second side surfaces both being in contact with the top and bottom surfaces, wherein ( i) the first and second side surfaces have a maximum separation w 1 at the front surface and (ii) a maximum separation w 2 at the rear surface, w, being smaller than w 2 . and both w, and vv 2 being measured parallel to a third axis simultaneously perpendicular to the first and second axes. In a preferred embodiment relating to a fluid cat cracking process, the invention comprises the steps of: (a) separately passing two streams of a two-phase fluid comprising a gas phase and a liquid phase comprising hot FCC feed oil, into an impingement mixing zone under pressure, in which a portion of each stream impingement mixes with the other, to form a single, impingement mixed fluid stream, in which the surface area of the liquid phase is increased to be greater than that in both streams prior to mixing; (b) passing the mixed stream formed in (a) into a shear mixing zone, downstream and adjacent to the impingement mixing zone with which it is in direct fluid communication, to further mix the mixed stream, primarily by shear mixing, to further increase the surface area of the liquid phase: (c) atomizing the shear mixed stream, by passing it through an atomizing means and into a lower pressure expansion zone in which said gas expands and forms a spray comprising drops of the atomized liquid, and (d) conducting the atomized spray through a spray distributor into a riser reaction zone, in which it contacts a particulate. hot. regenerated cracking catalyst, at reaction conditions effective to catalvtically crack the oil and produce lower boiling hydrocarbons, the spray distributor being a three dimensional member having ( 1 ) a front surface separated from a rear surface by a length L along a first axis and (2) a continuous, internal, fan-shaped channel open at the front and rear surface, the channel having (a) flat, parallel top and bottom surfaces separated by a constant height h measured parallel to a second axis perpendicular to the first axis and (b) curved first and second side surfaces both being in contact with the top and bottom surfaces, wherein (i) the first and second side surfaces have a maximum separation w, at the front surface and (ii) a maximum separation w 2 at the rear surface. W| being smaller than w 2 , and both w, and w 2 being measured parallel to a third axis simultaneously perpendicular to the first and second axes. The lower boiling hydrocarbons are recovered and typically at least a portion are upgraded by one or more upgrading operations, such as tractionation. The cracking reaction produces spent catalyst particles, which contain strippable hydrocarbons and coke, as is known. The lower boiling hydrocarbons are separated from the spent catalyst particles in a separation zone and the spent catalyst particles are stripped in a stripping zone, to remove the strippable hydrocarbons to produce stripped, coked catalyst particles. The stripped, coked catalyst particles are passed into a regeneration zone, in which they are contacted with an oxygen-containing gas. at conditions effective to burn off the coke and produce the hot. regenerated catalyst particles, which are then passed back up into the riser reaction zone. BRIEF DESCRIPTION OF THE DRAWINGS Figures 1 (a) through 1 (d) schematically illustrate various views of an atomizing nozzle of the invention, with Figures 1 (a) and 1 (c ) being respective views from the upstream and downstream ends of the nozzle. Figure 1 (b) being a cut-away side view and Figure 1 (d) a partial cut-away top view. Figures 2 (a) through 2 (d) schematically illustrate the nozzle of Figure 1 fabricated of stacked metal platelets, including an atomizing distributor as part of the nozzle. Figures 3 (a) through 3 (d) schematically illustrate various views of another embodiment of an atomizing nozzle of the invention, with Figures 3 (a) and 3 (c) being respective views from the upstream and downstream ends of the nozzle. Figure 3 (b) being a cut-away side view and Figure 3 (d) a partial cutaway top view of Figure 3 (c). Figures 4 (a) through 4 (c) schematically illustrate three different views and a combination of the nozzle of Figure 3 and a preferred spray distributor. Figure 5 is a cut-away schematic view of an atomizing nozzle and tip in association with an upstream fluid conduit. Figures 6 (a) through 6 (c) are views of an atomizing nozzle means of the invention similar to that illustrated in Figures 3 and 4. but wherein the shear mixing zone includes an atomizing orifice. Figure 7 is a schematic side view of an FCC feed injection unit employing a nozzle of the invention. Figure 8 is a simplified schematic of a fluid cat cracking process useful in the process of the invention. DETAILED DESCRIPTION The two-phase fluid fed into the mixing nozzle may be gas-continuous or liquid-continuous, or it may be a bubbly froth, in which it is not known with certainty if one or both phases are continuous. This may be further understood with reference to. for example, an open cell sponge and a closed cell sponge. Sponges typical lyjiave a 1 : 1 volumetric ratio of air to solid. An open cell sponge is both gas (air) and solid continuous, while a closed cell sponge is solid continuous and contains discrete (dispersed) gas cells. In an open cell sponge, the solid can be said to be in the form of membranes and ligaments (such as may exist in a two-phase gas-liquid froth or foam). In a closed cell sponge, the gas can be envisioned as in the form of a dispersion of discrete gas globules in the solid. Some sponges fall in-between the two. as do some two-phase fluids comprising a gas phase and a liquid phase. It is not possible to have a sponge that is gas-continuous and not also solid-continuous, but it is possible to have a two-phase gas and liquid fluid that is gas-continuous only. Therefore, the particular morphology of the fluid as it is passed into and through the mixing nozzle of the invention, is not always known with certainty. Irrespective of this, for this embodiment of the invention, there must be sufficient gas present in the fluid entering the nozzle, for the impact and shear mixing to increase the surface area of the liquid phase. This is reflected in reducing (i) the thickness of any liquid membrane, (ii) the thickness and/or length of any liquid rivulets, and (iii) the size of any liquid globules in the fluid, either before or during the atomization. In the practice of the invention, impingement and shear mixing in the nozzle and through orifices will only occur with a two-phase fluid comprising a gas phase and a liquid phase. It is preferred that the fluid comprise mostly gas on a volumetric basis (e.g.. a volumetric gas to liquid ratio of at least 2: 1 ) for efficient shear mixing. A single phase fluid (e.g.. liquid) passed through the nozzle, will have its kinetic energy increased directly proportional to the pressure drop across the nozzle. With a two-phase fluid comprising a gas phase and a liquid phase, the gas velocity is increased relative to the velocity of the liquid phase, ( i) in the impingement mixing zone, (ii) in the nozzle shear mixing zone, and (iii) when the fluid passes through an orifice of smaller cross-section perpendicular to the fluid flow direction than the fluid conduit means upstream of the orifice ( a pressure-reducing orifice). This velocity differential between the gas and liquid phases results in ligamentation of the liquid, particularly with a viscous liquid, such as a hot FCC feed oil. By ligamentation is meant that the liquid forms elongated globules or rivulets. The velocity differential is decreased during shear mixing. Thus, passing a two-phase fluid through a pressure-reducing orifice or impingement mixing it, produces a velocity differential between the gas and liquid which results in ligamentation of the liquid and/or dispersion of the liquid in the gas due to shearing of the liquid into elongated ligaments and/or dispersed drops. Additional shear of the liquid occurs when the fluid enters the orifice entrances of the nozzle and through the atomizing orifice. This additional shear also adds to reduction of the ultimate droplet size of the oil droplets in the atomized spray. The atomizing zone is at a lower pressure than the pressure upstream of the atomizing orifice. Consequently, the gas in the fluid passing through the atomizing orifice rapidly expands, thereby dispersing the liquid rivulets and/or droplets into the atomizing zone. Any rivulets break into two or more droplets during the atomization. The atomizing orifice may be a discrete, readily discernable orifice downstream of the shear mixing zone, or it may be in the form of a region or zone of the smallest cross-sectional area in the shear mixing zone. In the later case, fluid atomization begins in the shear mixing zone of the nozzle. In the strictest technical sense, atomization sometimes refers to increasing the surface area of a liquid and this occurs when the steam or other atomizing gas is mixed with, or injected into, the liquid to be atomized. However, in the context of the invention, atomization means that as the fluid passes through the atomizing orifice, the liquid phase breaks up. or begins to break up. into discrete masses in the gas phase and this continues as the fluid continues downstream and the liquid is atomized into a spray of droplets dispersed in the gas phase. Referring now to Figure 1. there are shown four different schematic views of an embodiment of an atomizing nozzle of the invention 10. Thus, nozzle 10 is shown as a cylindrical body 12. the interior of which comprises a single. unitary and generally longitudinal cavity 14. open at both ends and having a longitudinal axis coincident with the longitudinal axis of the nozzle. The upstream and downstream ends of cavity 14 are located at the respective upstream 16 and downstream 18 ends of the nozzle, for fluid to flow through. Cavity 14 is generally rectangular in cross-section normal to the longitudinal axis and is divided into three sequential zones, all of which are in fluid communication, with adjacent zones in direct fluid communication. Beginning at the upstream end and progressing downstream, cavity 14 comprises a fluid expansion zone 20. followed by an impingement mixing zone 22 and then a shear mixing zone or throat portion 24. The upstream opening of the cavity comprises a pair of symmetrically identical and circle segment-shaped fluid openings 26 and 26 * . separated in this embodiment by a fluid stream splitting means 28. Means 28 in this embodiment comprises a generally rectangular shaped plate, which bisects the circular entrance end of the nozzle, for splitting a stream of flowing fluid just upstream of the nozzle, into two separate and equal streams, which pass into and through the fluid openings 26 and 26 " . Each of the two parallel edges of the plate form the chordal portion of each respective fluid entrance. The downstream end of the cavity 14 comprises a non-circular exit orifice 30. In this embodiment the orifice is shown to be square-shaped, although other shapes may also be employed. A non-circular orifice is preferred. This exit orifice may or may not comprise at least a portion of the atomizing means. Cavity 14 is formed by two different pairs of opposing walls ( 36-38-23) - ( 36 * -38 ' -23 " ) and 34-34 ' . as shown. Walls 34 and 34 ' are identical, flat, parallel and are rectangular in shape, while 36-38-23 and 36 ' -38'-23 " are symmetrical. The same point on a wall pair is equidistant from the longitudinal axis for each wall, with the intersection of walls (36-38-23)-34 and (36 " -38 " - 23 " )-34 ' each forming a right angle. Walls 36-38-23 and 36 " -38 " -23 ' each begin upstream with an arcuate or circular shape perpendicular to the longitudinal axis of the nozzle, substantially conforming to the circular shape of the upstream feed conduit and the fluid entrances of the nozzle. This shape is maintained until the steps 38-38' at the entrance to the throat portion 24 is reached, at which point it changes to a flat shape which continues (23 and 23 ') until it terminates in the square-shaped exit 30. to more effectively utilize the impingement momentum. This produces a more uniform size distribution of the atomized oil droplets, than a circular or arcuate exit would. The two symmetrically identical and segment- shaped fluid openings 26 and 26'. are diametrically opposite and radially spaced apart, equidistanrfrom the longitudinal axis. The combined cross-sectional areas of these two segment-shaped fluid openings is smaller than that of the small expansion zone 20. but larger than the rectangular opening of the impingement mixing zone immediately downstream of 20. in order to reduce the pressure drop of the fluid entering into the mixing zones. By cross-sectional area is meant the cross-sectional area normal to the average fluid flow through the nozzle. In this embodiment, it is also the cross-sectional area normal to the longitudinal axis of the nozzle and this is ty pical for a nozzle of the invention. Hereinafter, all references to cross-sectional area will refer to the area normal or perpendicular to the direction of fluid flow. In this embodiment and in any typical embodiment of the invention, the fluid openings into the cavity will be velocity- increasing fluid openings, because of their smaller cross-sectional area compared to that of the flowing fluid stream, before being split into two separate streams. This can be seen, for example, in Figure 5. Looking at Figure 1 (b). a two-phase fluid stream comprising a gas phase and a liquid phase comprising the liquid to be atomized, flowing from upstream into and through cavity 14 in nozzle 10. is forced to split into two equal streams by means 28. with each split stream entering into the nozzle through respective opening pairs 26 and 26 " . in the upstream end 16 of the nozzle. In the embodiment shown in Figure 1 (a), the pressure drop due to the impingement onto the splitting means 28 ma be too high for some applications and, hence, a lower pressure drop means for introducing fluid into the nozzle can be employed. Thus, two separate fluid streams from any convenient source and comprising a two-phase mixture of a gas phase and a liquid phase, may be fed into the nozzle, at two radially spaced apart and substantially equal size fluid openings. In this embodiment, the two separate feed lines feeding the fluid two separate nozzle inlets, have to be sized so as to achieve the desired fluid inlet velocity. Looking at Figure 1 (b). each split stream is introduced into a respective top and bottom of the cavity, through the velocity-increasing openings 26 and 26'. As the fluid flows through each opening into the cavity, its velocity is increased because of the smaller cross- sectional area of the openings compared to that of the upstream conduit. This results in shearing forces because the lighter gas phase accelerates more quickly than the heavier liquid phase. After this, each fluid stream passes into the expansion zone, which is a controlled expansion zone 20 ( 1 10 in Figure 3(b) and Figure 3 (d)). in the sense that the fluid is not permitted to freely expand, as it is in an atomizing zone. This slight expansion zone between the two fluid entrances and the upstream end of the impingement mixing zone, reduces the pressure drop from what it would otherwise be if the expansion zone was not present. The outer peripheral portion of both flowing fluid streams impacts or impinges directly onto the right angle steps 38-38' and is forced radially inward to impinge directly into each other in impingement zone 22. In this embodiment in which steps 38-38 ' are both at right angles to the longitudinal axis of the nozzle and cavity, the included angle between the impinging fluids is 180°. Thus, the fluid impacting plane, taken as vertical in the drawing, is normal to the longitudinal axis of the nozzle. This radial, right angle impingement directs the radially inward component of both streams to a point on the longitudinal axis, which produces the maximum impingement mixing possible. As the fluid continues downstream, it enters the shearing zone whose cross-sectional area decreases in the downstream direction, to increase the flow velocity and further reduce the size of the liquid globules, primarily by shearing. While there is no abrupt change from the impingement mixing zone to the shear mixing zone, in this embodiment, mostly shear mixing begins downstream of the steps 38-38'. One pair of opposing walls 23 and 23 ' defining the shear mixing zone, are sloped and converge inward in the downstream flow direction, to the square exit orifice 30. The gradual decrease in the cross-sectional area of the shear mixing zone from this downstream wall convergence results in an increase in fluid flow velocity, with the maximum velocity achieved at the downstream nozzle exit orifice 30. Nozzle 10 can be fabricated in a number of different ways, at the discretion of the " practitioner. Thus a lost wax or investment casting process could be employed, as well as forging and other casting processes. The nozzle may be fabricated of a ceramic, metal or combination thereof. Fabrication of a nozzle using a plurality of stacked, relatively thin metal plates or platelets, in order to form an article having fluid passage means therein, is known and disclosed as useful for rocket motors and plasma torches in. for example. US Patents 3.881.701 and 5.455.401. This fabrication technique is also useful in fabricating nozzles of the invention, including the embodiments generally disclosed and shown in Figures 1-6. and nozzles of the invention have been fabricated using this technique. However, the invention is not intended to be limited to the use of this technique for nozzle fabrication. Figure 2 ( a) schematically illustrates a cross-sectional side view of nozzle 10 of Figure 1. fabricated of a plurality of stacked metal platelets. 50-62. The individual metal platelets are prepared having the required cavities and any other passages therein, as holes, slots or orifices extending through the platelet. They are then stacked together, bolted and/or diffusion bonded together, to form the final nozzle. Thus, in Figure 2 (a), starting from the upstream end of the nozzle, platelet 50 comprises a disk having the two circle segment-shaped openings in it defined by the stream splitting plate 28. as illustrated in Figure 1 ( a). Figure 2 (d) schematically illustrates disk 56. which includes the shoulders 38 and 38 " . In Figure 2 (d). disk 56 is a solid metal disk having a generally rectangular cavity 15 in its center portion. This illustrates the relative size and shape of the cavity 14, adjacent the impingement mixing shoulders. The gradual decrease in the distance between opposite sides of the converging walls (the vertical size of the opening in each platelet), starting with 57 and proceeding to 62. approximates the opposing, flat angled throat wall sections 23 and 23 ' . illustrated in Figure 1 (b). While each of the radially inward steps of each successive disk 57-62 is not large enough to impart as much radially inward momentum to the flowing fluid, as in the case of disk 56. they do continue to impart a radially inward, impingement mixing component to the flowing fluid. Figure 2 (a) also includes an atomizing spray distributor 64 (also referred to herein as a 'tip" or "fan tip") at the downstream end of the nozzle, for producing a generally flat and fan-shaped spray of the atomized liquid. Other views of tip 64 are shown in Figures 2 (b) and 2 (c). This unit is welded, bolted, brazed or otherwise attached to the nozzle, thereby forming a part of the nozzle. In this embodiment, distributor 64 includes a flange 63 for attachment to a nozzle. The flange has an orifice 70 in its center, normal to the fluid flow direction adjacent to. and the same size and shape as the nozzle exit (30 in Figure 1). Orifice 70 opens up downstream into a generally flat and divergent fan-shaped channel forming a spray distribution tip. defined by opposing wall pairs 66-66' and 74-74 " . which define a fan-shaped atomizing zone 68. The channel is open at its front surface ( i.e. the upstream end of the channel) and at its rear surface (i.e. the downstream end of the channel). Zone 68 is seen slightly converging in the vertical direction proceeding downstream, as shown in Figure 2 (a), to control the rate of shear mixing while the flow is diverging in the horizontal direction, as shown in Figure 2 (c). The tip ends downstream in orifice 72. which is oriented normal to the outward flow spray direction and has its longest dimension generally perpendicular to the impingement fluid flow direction imparted by 38-38 " . The fluid exiting the orifice 30 of the nozzle, enters into the controlled expansion zone 68. through orifice 70. This further shears the fluid, as mentioned above, thereby further reducing the drop size of the liquid dispersed in the fluid. Expansion zone 68 is at a lower pressure than that upstream of orifices 30 and 70. with the result that the gas phase rapidly expands and atomizes the liquid to produce a spray of the atomized liquid droplets. This further shears the liquid droplets and the fan shape of the atomizing tip produces a fan-shaped spray of the liquid droplets, which continue through zone 68 and into the lower pressure downstream location shown in Figure 7. Figure 3, schematically illustrates another embodiment of an atomizing nozzle 100 of the invention. In this embodiment, as in the other embodiments of an impingement and shear mixing nozzle of the invention shown in the Figures, each split stream enters the interior cavity of the nozzle substantially parallel to the overall fluid flow direction, which is parallel to the longitudinal axis of the cavity and. in these embodiments, also the nozzle. These streams are equal, symmetrical and enter the cavity at a respective top and bottom, being diametrically separate and opposed, as shown. In the impingement mixing portion of the cavity, a radially inward flow component, normal to the longitudinal axis, creates the impingement mixing. The single stream formed in the impingement mixing zone or portion, flows generally parallel to the longitudinal axis in the shear mixing zone and out of the nozzle. A view of the nozzle from the upstream end and a side view in partial cut-away fashion are respectively shown in Figures 3 (a) and 3 (b). Thus, nozzle 100 is shown as a cylindrical body 102 containing a single, longitudinal cavity 104 within, being symmetrical about its longitudinal axis, which is coincident with the longitudinal axis of the nozzle. Cavity 104 is open at both ends for fluid to flow through. with its fluid entrance and exit ends, extending through the tluid upstream 106 and exit downstream 108 ends of the nozzle, as shown. Cavity 104 comprises a sequence of three zones, all in fluid communication with each other. Starting at the upstream end of the cavity they are. (i) a fluid expansion zone 1 10. ( ii) a fluid impingement mixing zone 1 12 and a tluid shear mixing zone 1 14. with the impingement and shear mixing zones having substantially rectangular cross- sections. As is the case for the nozzle of Figure 1. the fluid passed from upstream into nozzle 100 is a two-phase fluid comprising a gas phase and a liquid phase comprising the liquid desired to be atomized. The upstream end 106 of the nozzle contains a pair of symmetrically identical fluid entrance orifices 1 16 and 1 16 " . diametrically opposed and radially spaced apart, equidistant from the center and in the shape of a segment of a circle. As is the case for the nozzle of Figure 1, in this embodiment the two fluid entrances are also radially equidistant from the center and separated by a generally rectangular stream-splitting plate 1 18. which bisects the circular entrance end of the nozzle, and with each of the two parallel edges 1 19 and 1 19' of the plate, forming the chordal portion of each respective fluid entrance. Thus, a fluid flowing from upstream into the nozzle is split into two identical streams, each of which passes into and through a respective fluid entrance 1 16 and 1 16 " and into the interior of the nozzle. In this embodiment, and as is shown in Figure 4. the cross-sectional area of each fluid entrance is less than half that of the upstream fluid conduit. This means that the velocity of each of the two streams entering a respective entrance is greater than that immediately upstream. This produces a shearing action on the two-phase fluid, thereby increasing the surface area of the liquid phase. Looking at Figures 3 (b). Figure 4 (a) and Figure 5. a fluid stream flowing into and through nozzle 100 is forced to split into two equal streams by means 1 18. each of which enters into the nozzle through respective equal size orifices 1 16 and 1 16 " . While splitting a single fluid stream into two separate streams in this fashion is convenient, the invention is not limited to this embodiment. In the embodiment shown in Figure 3. the pressure drop due to the impingement onto the splitting means may be too high for some applications. A lower pressure drop means can be employed or two separate streams from any convenient source may be fed into the upstream end of the chamber 1 4. and preferably through shear-inducing orifices. Also, as is the case for the nozzle of Figure 1. the cross-sectional area relationships of the tluid entrances, the expansion zone 1 10 and the upstream opening of the impingement mixing zone also apply here. As each fluid stream enters into the open-ended, unitary and singular cavity 104 longitudinally extending through the nozzle, it immediately enters into the expansion zone 1 10 just upstream of the impingement mixing zone 1 12. so that it can be turned radially inward without an excessive pressure drop. This is not an uncontrolled expansion, but it minimizes coalescence of the smaller liquid drops formed by passing the fluid through the entrances. As each stream continues downstream, the circumferentially outer portion contacts a means which imparts a radially inward flow component to it. thereby forcing a portion of each stream to flow radially inward, where it impinges and impacts the radially inward flow from the other stream, head on. This causes violent and chaotic mixing, which converts kinetic energy into increased liquid phase surface tension energy, as reflected in an increase in the surface area of the liquid phase. This surface area increase ultimately manifests itself as smaller liquid droplets in the final atomized liquid spray. Two arcuate, circumferential or peripheral shoulders. 122 and 122". extending radially inward from walls 125 and 125 * . impart the radially inward flow component to each tluid stream as it impinges upon each shoulder, thereby forcing a portion of each stream against a portion of the opposite stream being directed towards it. Thus, the radially inward flows are directed against each other in a head-on fashion, thereby producing violent and turbulent mixing to further increase the surface tension energy of the liquid phase of the fluid. This inward flow component is normal to the longitudinal axis of the nozzle. The plane of both of the shoulders 122 and 122 ' is normal to the longitudinal nozzle axis and parallel to the flat ( 106 and 108) ends of the nozzle and. therefore, concomitantly parallel to the fluid exit orifice 128 of the nozzle and mixing cavity. Although slight divergence from normal can be tolerated, it is preferred that the plane of the shoulder surface be within 90 υ ± 5° of the longitudinal axis of the nozzle. This is also the case for the nozzle of Figure 1. It is preferred in the practice of the invention that the tluid exit orifice of the nozzle not be circular for the reasons given previously. Thus, the exit orifice 128 will have one dimension longer than the other, and it is preferred that the longer dimension of the generally rectangular-shaped impingement mixing zone be normal or perpendicular to the longest dimension of the fluid exit orifice. The turbulent fluid passes from the impingement mixing zone into and through the shear mixing zone 1 14. which may also be referred to as a throat. This zone is also formed by two pairs of opposing and generally parallel walls 130- 130' and 126- 126', which intersect at a 90° angle, to form the generally rectangular-shaped cross-section. As is shown in Figures 3 (b) and 3 (d). the shear mixing zone in this embodiment is defined by these two pairs of radially opposite and opposing walls, one pair of which. 126 and 126 " . converge inward in the downstream flow direction and the other pair of which. 130 and 130 " . diverge outward in the downstream flow direction. The net effect is either a generally overall constant cross-section of the shear mixing zone normal to the tluid flow, or one that converges and then diverges by from about 10-50% larger than the minimum cross-sectional area. For this embodiment, it will be taken as a generally constant cross-section. This design of diverging and converging walls produce a shear mixing zone having a lower fluid pressure drop through it. than the embodiment illustrated in Figure 1. It also reduces the possibility of coalescence in the shear mixing zone, as compared to that shown in Figure 1. The orifice entrance 132 to the shear mixing zone 1 14 is defined by the radially inward edge of shoulders 122- 122' and the intersection of walls 124- 130 and 124'- 130' . The cross-sectional area of the orifice entrance to the shear mixing zone is smaller than that of the combined areas of 1 16 and 1 16 " . This increases the velocity of the fluid as it flows into the shear mixing zone. In this embodiment, the divergence and convergence of the two pairs of opposing walls of the shear mixing zone shape the fluid flow into a generally rectangular shape at the exit orifice 128. as is shown in Figure 3 (c). This is done to accommodate the flow from the nozzle 100. smoothly into the atomizing spray distribution tip 150. as shown in Figure 4. Thus, turning to Figures 4 (a). 4 (b) and 4 (c). it is seen that these Figures are similar to Figures 3 (b). 3 (c) and 3 (d). respectively, with the exception of the atomizing spray distribution tip 150 adjacent and attached to the downstream orifice exit of the nozzle 102 in Figure 4. This was omitted from Figure 3. for clarity and ease in understanding the invention. Thus, atomizing spray distribution tip 150 comprises a generally fan-shaped body 152 containing a fan- shaped channel or cavity 154 within, defined by opposing and outwardly diverging walls (side walls) 155 and 155 * . which serves to control the expansion of the atomizing tluid. into a fan-shaped spray. As discussed, the walls may be curved in a direction approximately perpendicular to the divergence. Preferably the side walls' curvature is such that the volume of the channel is increases, as shown in figure 4(b). The fluid entrance 158 of the tip is an opening in the front (i.e. upstream) end of the channel and corresponds in shape to the fluid exit 128 of the nozzle to which it is attached. The exit 160 of the tip is an opening in the rear ( i.e. downstream) end of the channel which is larger in order to permit the atomized spray of liquid drops to continue expanding into a fan-shaped spray. The pressure in 154 is lower than that in the nozzle cavity. Accordingly, the side walls are separated by a width w, at the channel's front surface and a width w 2 at the channel's rear surface. In cases where curved side walls are employed, vv, and w 2 are measured where the side wall separation is the widest, which will usually be the center of the channel measured along a line separating the channel's top surface from the bottom surface. Preferably, w, is at least about 1.5(L). where L is the length of the channel measured from the front to the rear surface in a direction approximately parallel to tluid flow. Preferably. is at least about 1.5(w, ). It should be noted that while flat, parallel top and bottom channel surfaces are generally preferred, they may be curved. Further, they may diverge in a fan- shaped manner with the separation increasing from upstream to downstream. It should also be noted that while the side walls will generally have the same curvature, the curvatures may be independently selected. Preferably, the curvature is circular ( i.e. in one view the side is an arc of a circle, as shown in figure 4(b), and the radius of curvature of either side wall may be independently selected. The preferred radius of curvature is about h/2 where h is the height of the channel in the direction approximately parallel to the side walls and approximately perpendicular to fluid flow. While not required, the center of each side wall's radius of curvature is generally located near a line parallel to the top and bottom surfaces, the line being preferably located at the midpoint between the upper and lower surfaces and approximately perpendicular to the direction of fluid flow in the channel. The mixed fluid exiting the nozzle into the lower pressure atomizing cavity 154. atomizes into a fan-shaped spray of liquid droplets, which continue out of the exit end 156 of the tip and into a riser reaction zone of an FCC unit, such as that shown in Figure 7. Figure 5 schematically illustrates a cut-away view of an atomizing nozzle and tip. in association with an upstream tluid conduit. Fluid conduit 164 provides the flow path for the fluid from an upstream source to be split into two separate and equal fluid streams, which pass into the respective nozzle entrances 1 16 and 1 16 " . Figure 6 is another embodiment of an atomizing nozzle of the invention in which the shear mixing zone is actually a compound zone which includes both shear mixing and atomization. by virtue of an atomizing zone in the shear mixing zone. Atomizing nozzle 170 shown in Figure 6 is identical to nozzle 100 shown in Figures 3 and 4. except for the shape of the fluid inlet orifices and shear mixing zone. Thus, nozzle 170 includes a cylindrical body 172 containing a unitary cavity 174 within, for impact and shear mixing the two-phase tluid flowing through the nozzle. As shown in Figure 6 (a), fluid inlets 1 17 and 1 17 ' need not be complete segments, if the upstream feed conduit (e.g.. 164 in Figure 5) is sufficiently large to allow an acceptable nozzle entry pressure drop. The shear mixing zone 1 15. has a complex shape in which the cross-sectional area of the zone, starting upstream at 121 and 121 '. at first decreases and then increases, prior to the downstream fluid exit 128. Two partial cross-section views of the nozzle taken at 6 (b) - 6 (b) and 6 (c) - 6 (c) are shown in Figure 6 (b) and Figure 6 (c), to illustrate the somewhat complex nature of the shear mixing zone. In this embodiment, the atomizing zone comprises the region or zone of smallest cross-sectional area within the shear mixing zone and occurs between the beginning of the shear mixing zone at 121-121 ' and exit orifice 128. Orifice 128 is of the same size and shape as that in the nozzle illustrated in Figures 3 and 4. The shear mixing zone in this embodiment, also includes an atomizing means in the form of the zone of smallest cross-sectional area. In operation, as the two- phase fluid flows through the orifice and into a lower pressure atomizing zone downstream, atomization is promoted by the rapid gas expansion in the lower pressure in the atomizing zone and also by the more rapid acceleration of the lighter, compressible gas than the higher density (and incompressible) liquid phase. This induces shear until their velocities more nearly equalize. This shear further decreases the ultimate size of the oil droplets in the atomized spray. Referring now to Figure 7. an FCC feed injection unit 180 useful in the practice of the invention comprises a hollow feed injector 182. attached to a nozzle means 184. by means of respective flanges 186 and 188. Nozzle means 184 is shown as a conduit penetrating through the wall 190 of an FCC riser and into the riser reaction zone 192. The riser is a cylindrical, hollow, and substantially vertically oriented conduit, in a portion of which (the riser reaction zone ) the atomized oil feed contacts the uprising, hot catalyst particles and is cracked into more useful, lower boiling hydrocarbon products Only a portion ot the riser conduit is show n tor convenience. The teed injector means 182 comprises a hollow conduit 194. into which the preheated oil teed is introduced via feed line 196. w hich torms a F-)unctιon with the wall ot the upstream portion of the injector. The downstream portion of the injector terminates in an impingement and shear mixing nozzle 100 of the invention, having a fan-shaped atomizing tip or distributor 150 as is illustrated in Figure 4. both of which are shown as boxes for convenience. The fan-shaped distributor 150 produces a relatively flat, fan-shaped spray of the atomized oil into the riser reaction zone 192. A steam sparging conduit 198, having a smaller diameter or cross-sectional area than the injector conduit 194. extends into and is axially aligned with the longitudinal axis of conduit 194. In this embodiment, the central, longitudinal axes of both conduits are coincident. This provides an annular flow path 197 for the hot oil. upstream ot the exit end of the injector. Steam conduit 198 terminates inside conduit 194. upstream of the nozzle 100. It should be noted that steam may also or alternatively be mixed with the feed external to the nozzel. as shown in figure 8. A plurality of holes or orifices 199. radially drilled circumferentially around the downstream end portion of 198. provide the means for sparging jets of steam radially out and into the annularly surrounding, hot oil flowing downstream towards the atomizing end of the injector. This produces a two-phase fluid comprising globules of hot oil dispersed in steam The amount of steam sparged into the oil is typically between 1 and 5 wt % of the hot oil feed. The resulting fluid mixture, which may typically comprise, on a v olume basis. 75-85 % steam and 15-25 % oil. is passed to the nozzle 100 which splits it into two separate steams which separately enter the nozzle. The two streams are impingement mixed in the nozzle to form a single stream, which continues into and through the shear mixing zone in the nozzle. The mixing in the nozzle substantially reduces the size ot the oil drops dispersed in the steam. As the fluid exits the orifice at downstream end of the nozzle, which is an atomizing orifice, it passes into the lower pressure controlled expansion zone defined by the interior of the atomizing tip. The atomizing orifice and controlled expansion zone (shown in Figure 4) are both in fluid communication with the lower pressure riser reaction zone 192. The atomized spray of oil drops proceeds into the riser reaction zone 192. in which it contacts an upflowing stream of hot catalyst particles (not shown), which catalvtically crack the heavy oil feed into the desired lower boiling product fractions. Figure 8 is a simplified schematic of a fluid cat cracking process used in conjunction with a feed injection method and atomizing nozzle means of the invention. Thus, an FCC unit 200 useful in the practice of the invention is shown comprising a catalytic cracking reactor unit 202 and a regeneration unit 204. Unit 202 includes a feed riser 206. the interior of which comprises the reaction zone, the beginning of which is indicated as 208. It also includes a vapor- catalyst disengaging zone 210 and a stripping zone 212 containing a plurality of baffles 214 within, in the form of arrays of metal "sheds' " which resemble the pitched roofs of houses. A suitable stripping agent such as steam is introduced into the stripping zone via line 216. The stripped, spent catalyst particles are fed into regenerating unit 204 via transfer line 218. A preheated FCC feed is passed via line 220 into the base of riser 206 at feed injection point 224 of the fluidized cat cracking reactor unit 202. The feed injector shown in Figure 6 is located at 224. but is not shown in this Figure, for simplicity. In practice, a plurality of feed injectors will be circumferentially located around the feed injection zone of the riser. The feed injectors will be of the type illustrated in Figure 7. Steam is injected into the feed injection unit via line 222. As set forth below, the feed may comprise a mixture of a vacuum gas oil (VGO). a heavy feed component, such as a resid fraction, and mixtures thereof. The atomized droplets of the hot feed are contacted with particles of hot. regenerated cracking catalyst in the riser. This vaporizes and catalvtically cracks the feed into lighter, lower boiling fractions, including fractions in the gasoline boiling range (typically 100-400 F), as well as higher boiling jet fuel, diesel fuel, kerosene and the like. The cracking catalyst is a mixture ot silica and alumina containing a zeolite molecular sieve cracking component, as is known to those skilled in the art The catalvtic cracking reactions start w hen the teed contacts the hot catalyst in the riser at teed in|ection point 234 and continues until the product vapors are separated from the spent catalyst in the upper or disengaging section 210 ot the cat cracker The cracking reaction deposits strippable hydrocarbonaceous material and non- stπppable carbonaceous material known as coke, to produce spent catalyst particles which must be stripped to remove and recover the strippable hydrocarbons and then regenerated by burning off the coke in the regenerator Reaction unit 202 contains cyclones (not shown) in the disengaging section 210. which separate both the cracked hydrocarbon product vapors and the stripped hydrocarbons (as vapors) from the spent catalyst particles. The hydrocarbon vapors pass up through the reactor and are withdrawn via line 226 The hydrocarbon vapors are typically fed into a distillation unit (not shown) which condenses the condensable portion ot the \apors into liquids and fractionates the liquids into separate product streams The spent catalyst particles tall down into stripping zone 212 in which they are contacted with a stripping medium, such as steam, which is ted into the stripping zone via line 216 and removes, as vapors, the strippable hvdrocarbonaceous material deposited on the catalvst during the cracking reactions These vapors are withdrawn along with the other product \ apors via line 226 The battles 214 disperse the catalyst particles uniformly across the width ot the stripping zone or stripper and minimize internal refluxing or backmixing ot catalyst particles in the stripping zone The spent, stripped catalyst particles are removed from the bottom ot the stripping zone v ia transfer line 218. from which they are passed into fluidized bed 228 in regenerator 204 In the fluidized bed they are contacted with air entering the regenerator v ia line 240 and some pass up into disengaging zone 242 in the regenerator The air oxidizes or burns oft the carbon deposits to regenerate the catalyst particles and in so doing, heats them up to a temperature which typically ranges from about 950-1400°F Regenerator 204 also contains c\ clones (not shown) which separate hot regenerated catalyst particles from the gaseous combustion products ( t ue gas), which comprises mostly C0 2 CO. H 2 0 and N 2 and feed the regenerated catalyst particles back down into fluidized catalyst bed 228. by means of diplegs (not shown), as is known to those skilled in the art. The fluidized bed 228 is supported on a gas distributor grid, which is briefly illustrated as dashed line 244. The hot. regenerated catalyst particles in the fluidized bed overflow the weir 246 formed by the top of a funnel 248. which is connected at its bottom to the top of a downcomer 250. The bottom of downcomer 250 turns into a regenerated catalyst transfer line 252. The overflowing, regenerated particles flow down through the funnel, downcomer and into the transfer line 252 which passes them back into the riser reaction zone, in which they contact the hot feed entering the riser from the feed injector. The flue gas is removed from the top of the regenerator via line 254. While the spray distributor may be practiced in connection with the nozzle set forth in figures 1 through 7 and described in detail above, it should be pointed out that the spray distributor may be used in connection with any atomizing nozzle, particularly atomizing nozzles for use in FCC processes. In this regard, in an alternative embodiment the spray distributor may be used in connection with the FCC injection apparatus and method set forth in U.S. Patent No. 5.173.175. incorporated by reference herein. Cat cracker feeds used in FCC processes typically include gas oils, which are high boiling, non-residual oils, such as a vacuum gas oil ( VGO). a straight run (atmospheric) gas oil. a light cat cracker oil (LCGO) and coker gas oils. These oils have an initial boiling point typically above about 450 F (232 C). and more commonly above about 650°F (343°C). with end points up to about 1 150 υ F (621°C). as well as straight run or atmospheric gas oils and coker gas oils. In addition, one or more heavy feeds having an end boiling point above 1050 ϋ F (e.g.. up to 13()0°F or more) may be blended in with the cat cracker feed. Such heavy feeds include, for example, whole and reduced crudes, resids or residua from atmospheric and vacuum distillation of crude oil. asphalts and asphaltenes. tar oils and cycle oils from thermal cracking of heavy petroleum oils, tar sand oil. shale oil. coal derived liquids, syncrudes and the like. These may be present in the cracker feed in an amount of from about 2 to 50 v lume % of the blend, and more typically from about 5 to 30 volume %. These feeds typically contain too high a content of undesirable components, such as aromatics and compounds containing heteroatoms. particularly sulfur and nitrogen. Consequently, these feeds are often treated or upgraded to reduce the amount of undesirable compounds by processes, such as hydrotreating. solvent extraction, solid absorbents such as molecular sieves and the like, as is known. Typical cat cracking conditions in an FCC process include a temperature of from about 800- 1200 υ F (427-648 υ C), preferably 850- 1 150°F (454-621°C) and still more preferably 900- 1 150°F (482-621°C), a pressure between about 5- 60 psig, preferably 5-40 psig with feed/catalyst contact times between about 0.5- 15 seconds, preferably about 1 -5 seconds, and with a catalyst to feed ratio of about 0.5- 10 and preferably 2-8. The FCC feed is preheated to a temperature of not more than 850°F. preferably no greater than 800°F and typicalK within the range of from about 500-800 υ F. The invention will be further understood with reference to the following example. EXAMPLE In this experiment, an atomizing injector was used similar in design to that shown in Figure 7 and had an atomizing nozzle of the invention similar in design to that shown in Figure 4. The operation of this injector was compared to that of a commercially proven slot and fan design, similar to that shown in US patent 5.173.175. The commercial nozzle simulated a pipe with an end cap containing a rectangular, slotted orifice. Both nozzles included a fan-shaped spray distributor and were fabricated at a scale of one half the size of a typical commercial nozzle. The injector was the same for both cases, with the difference between them being in the nozzle design. Both injectors produced a tlat. fan-shaped spray and were mounted horizontally and oriented to produce a tlat. fan-shaped spray with the maximum width in the vertical direction, in the laser light beam path of a Malvern particle sizer. This instrument is well known and used for measuring liquid spray characteristics. Light diffraction patterns, each associated with a characteristic drop size range, are focused by a Fourier transform lens onto a multi-element photodetecter. The light energy distribution is-converted. via a computer, into a corresponding liquid droplet size distribution. A grid of comparative experiments was conducted varying water and nitrogen flow rates and the Sauter mean liquid drop diameter was calculated, assuming a Rosin-Rammier distribution function. The results for the two different nozzle designs are compared in the Table below. In all cases, at comparable water and nitrogen flow rates, the nozzle of the invention produced an atomized spray having smaller Sauter mean diameter liquid droplets, than did the commercial design. This shows that better atomization was achieved with the nozzle of the invention. It is understood that various other embodiments and modifications in the practice of the invention w ill be apparent to. and can be readily made by. those skilled in the art without departing from the scope and spirit of the invention described above. Accordingly, it is not intended that the scope of the claims appended hereto be limited to the exact description set forth above, but rather that the claims be construed as encompassing all of the features of patentable novelty which reside in the present invention, including all the features and embodiments which would be treated as equivalents thereof by those skilled in the art to which the invention pertains.

Claims: CLAIMS: 1. A spray distributor comprising: a three dimensional member having ( 1 ) a front surface separated from a rear surface by a length L along a first axis and (2) a continuous, internal, fan-shaped channel open at the front and rear surface, the channel having (a) flat, parallel top and bottom surfaces separated by a constant height h measured parallel to a second axis perpendicular to the first axis and (b) curved first and second side surfaces both being in contact with the top and bottom surfaces, wherein (i) the first and second side surfaces have a maximum separation w, at the front surface and (ii) a maximum separation w at the rear surface. W| being smaller than w 2 , and both W] and w 2 being measured parallel to a third axis simultaneously perpendicular to the first and second axes. 2. The spray distributor of claim 1 wherein W ! is at least about 1.5(L). 3. The spray distributor of claim 2 wherein w is at least about 1.5(w , ). 4. The spray distributor of claim 3 wherein the side surfaces have the same radius of curvature. 5. The spray distributor of claim 4 wherein the side surfaces have a radius of curvature of about h/2. 6. A fluid cat cracking process, the invention comprises the steps of: (a) separately passing two streams of a two-phase tluid comprising a gas phase and a liquid phase comprising hot FCC feed oil. into an impingement mixing zone under pressure, in which a portion of each stream impingement mixes with the other, to form a single, impingement mixed tluid stream, in which the surface area of the liquid phase is increased to be greater than that in both streams prior to mixing; (b) passing the mixed stream formed in (a) into a shear mixing zone, downstream and adjacent to the impingement mixing zone with which it is in direct fluid communication, to further mix the mixed stream, primarily by shear mixing, to further increase the surface area of the liquid phase; (c) atomizing the shear mixed stream, by passing it through an atomizing means and into a lower pressure expansion zone in which said gas expands and forms a spray comprising drops of the atomized liquid, and (d) conducting the atomized spray through a spray distributor into a riser reaction zone, in which it contacts a particulate. hot. regenerated cracking catalyst, at reaction conditions effective to catalvtically crack the oil and produce lower boiling hydrocarbons, the spray distributor being a three dimensional member having ( 1) a front surface separated from a rear surface by a length L along a first axis and (2) a continuous, internal, fan-shaped channel open at the front and rear surface, the channel having (a) flat, parallel top and bottom surfaces separated by a constant height h measured parallel to a second axis perpendicular to the first axis and (b) curved first and second side surfaces both being in contact with the top and bottom surfaces, wherein ( i) the first and second side surfaces have a maximum separation w, at the front surface and ( ii) a maximum separation w 2 at the rear surface, w, being smaller than w 2 . and both W| and w 2 being measured parallel to a third axis simultaneously perpendicular to the first and second axes. 7. The tluid cat cracking process of claim 6 wherein Wj is at least about 1.5(L). 8. The fluid cat cracking process of claim 7 wherein w 2 is at least about 1.5(w, ). 9. The fluid cat cracking process of claim 8 wherein the side surfaces have the same radius of curvature. 10. The fluid cat tracking process of claim 9 wherein the side surfaces have a radius of curvature of about h/2.

Inventors: ITO JACKSON I, ITO, JACKSON, I.
Applicants: EXXONMOBIL RES & ENG CO, EXXONMOBIL RESEARCH AND ENGINEERING COMPANY
Application year: 2000
Main classification: F23D14
IPC codes: B01J8, B01J19, B05B1, C10G11