Uniflow cyclone separator with stable vortex and tangential heavy phase extraction

Abstract

A uniflow cyclone that has multiple inlets, normally achieved via a vane, a barrel length, then a solids collection channel of larger diameter but concentric with the barrel and a tangential solids outlet to either a plenum or a dust hopper. The gas flows past the enlarged channel and continues through additional barrel length to an outlet zone. The cyclone would normally have a concentric center pipe the extends from the vane to the gas outlet of the cyclone.

Claims

1. A uniflow cyclone separator for removing solids from a vortex, the cyclone separator comprising: a first stage separator comprising: a barrel having first and second ends and comprised of a cylindrical wall having a predetermined height; a center pipe positioned within the barrel and extending for at least the entire height of the cylindrical wall; a gas inlet for injecting a fluid into the barrel proximate the first end; a vane attached to the center pipe proximate the gas inlet for initiating a vortex from the injected fluid; a peripheral channel positioned within the cylindrical wall proximate the second end of the barrel; and a tangential solids ejection port connecting the peripheral channel to a dust hopper; wherein, the vortex remains relatively undisturbed and continues through the barrel past the peripheral channel; and entrained solids within the vortex are removed by entering the dust hopper via the peripheral channel; a second stage separator stacked onto the first stage separator, the second stage separator comprising: an extension of the cylindrical wall from the second end to an extended end; an extension of the center pipe to extend the center pipe for at least the entire height of the cylindrical wall and the extension of the cylindrical wall; a second vane attached to the extension of the center pipe above the peripheral channel, the second vane being for maintaining the vortex of the injected fluid; a second peripheral channel positioned within the extension of the cylindrical wall proximate the second end of the barrel; and a second tangential solids ejection port connecting the second peripheral channel to a second dust hopper; wherein, the initiated and maintained vortex remains relatively undisturbed and continues through the barrel past the second peripheral channel; and entrained solids within the vortex are removed by entering the second dust hopper via the second peripheral channel.

2. The uniflow cyclone separator of claim 1, wherein the vortex is modified by the second vane with a pitch which will change the velocity in the vortex by changing the vortex angle.

3. A uniflow cyclone separator for removing solids from a vortex, the cyclone separator comprising: a first stage separator comprising: a barrel having first and second ends and comprised of a cylindrical wall having a predetermined height; a center pipe positioned within the barrel and extending for at least the entire height of the cylindrical wall; a gas inlet for injecting a fluid into the barrel proximate the first end; a vane attached to the center pipe proximate the gas inlet for initiating a vortex from the injected fluid; a peripheral channel positioned within the cylindrical wall proximate the second end of the barrel; and a tangential solids ejection port connected to the peripheral channel to eject entrained solids from the vortex; wherein the vortex remains relatively undisturbed and continues through the barrel past the peripheral channel; a second stage separator stacked onto the first stage separator, wherein the second stage separator comprises: an extension of the cylindrical wall from the second end to an extended end; an extension of the center pipe to extend the center pipe for at least the entire height of the cylindrical wall and the extension of the cylindrical wall; a second vane attached to the extension of the center pipe above the peripheral channel, the second vane being for maintaining the vortex of the injected fluid; a second peripheral channel positioned within the extension of the cylindrical wall proximate the second end of the barrel; and a second tangential solids ejection port connected to the second peripheral channel to eject entrained solids from the vortex; wherein the initiated and maintained vortex remains relatively undisturbed and continues through the barrel past the second peripheral channel.

4. The uniflow cyclone separator of claim 3, wherein the vortex is modified by the second vane with a pitch which will change the velocity in the vortex by changing the vortex angle.

5. A uniflow cyclone separator for removing solids from a vortex, the cyclone separator comprising: a first stage separator comprising: a barrel having first and second ends and comprised of a cylindrical wall having a predetermined height; a center pipe positioned within the barrel and extending for at least the entire height of the cylindrical wall; a gas inlet for injecting a fluid into the barrel proximate the first end; a vane attached to the center pipe proximate the gas inlet for initiating a vortex from the injected fluid; a peripheral channel positioned within the cylindrical wall proximate the second end of the barrel; and a tangential solids ejection port connecting the peripheral channel to a dust hopper; wherein, the vortex remains relatively undisturbed and continues through the barrel past the peripheral channel; and entrained solids within the vortex are removed by entering the dust hopper via the peripheral channel; a plurality of cyclone separator stages stacked consecutively onto the first stage separator, wherein each of the plurality of cyclone separator stages comprises: an extension of the cylindrical wall from a previous stage wall to an extended end; an extension of the center pipe to extend the center pipe for at least the entire height of the cylindrical wall and the extension of the cylindrical wall; a tertiary vane attached to the extension of the center pipe for maintaining the vortex of the injected fluid; a tertiary peripheral channel positioned within the extension of the cylindrical wall; and a tertiary tangential solids ejection port connected to the tertiary peripheral channel; wherein, the initiated and maintained vortex remains relatively undisturbed and continues through the barrel past each tertiary peripheral channel; and entrained solids within the vortex are removed by entering the tertiary peripheral channel.

6. A uniflow cyclone separator of claim 5, wherein the tertiary vane is located and angled to increase a tangential velocity of the vortex in consecutive stages.

7. A uniflow cyclone separator of claim 5, further comprising a tertiary dust hopper connected to the tertiary peripheral channel of at least one of the plurality of stages.

8. A uniflow cyclone separator of claim 5, further comprising an open area between two tube sheets positioned between consecutive stages of the plurality of stages, wherein entrained solids are ejected from the tertiary solids ejection port into the open area.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

(1) For the purpose of facilitating an understanding of the subject matter sought to be protected, there are illustrated in the accompanying drawings, embodiments thereof, from an inspection of which, when considered in connection with the following description, the subject matter sought to be protected, its construction and operation, and many of its advantages should be readily understood and appreciated.

(2) Note: all data used to prepare appended graphs and simulations is theoretical based on Eq. 3 and Eq. 4 above.

(3) FIG. 1 is a line chart showing typical grade efficiency curves predicted by Equation 3 for a single-stage cyclone operated at typical FCCU conditions based on vortex revolutions (1 rev. vs. 1.5 rev. vs. 2 rev.);

(4) FIG. 2 is a CFD simulation of a prior art primary cyclone operating at typical FCCU regenerator conditions showing velocity magnitudes;

(5) FIG. 3 is a CFD simulation of a prior art primary cyclone operating at typical FCCU regenerator conditions showing velocity profiles;

(6) FIG. 4 is a top view schematic of a 42.5 ft (OD) regenerator vessel with 17 sets of 55-inch diameter voluted cyclones of the prior art with six inches of clearance between the vessel ID and each cyclone;

(7) FIG. 5 is a schematic of a Third Stage Separator from U.S. Pat. No. 6,673,133 showing individual uniflow cyclones mounted in the separator vessel;

(8) FIG. 6A is a perspective view of an embodiment of the uniflow cyclone separator of the present invention;

(9) FIG. 6B is a perspective view of the embodiment of FIG. 6A with a section of the cyclone barrel removed;

(10) FIG. 6C is a perspective view of the embodiment of FIG. 6B rotated to show the peripheral channel and port leading to the dust hopper;

(11) FIG. 7 is a side view of the embodiment of FIG. 6A with a section of an outer surface of the dust hopper and peripheral channel removed;

(12) FIG. 8A is perspective view of an embodiment of a two-stage cyclone separator in accordance with the present disclosure;

(13) FIG. 8B is a side cross-section of the two-stage cyclone separator of FIG. 8A;

(14) FIG. 9 is a top view schematic of a 42.5 ft (OD) regenerator vessel housing 27 sets of cyclones of the present disclosure;

(15) FIG. 10 is a side schematic showing a height comparison between a classic two-stage cyclone set (left) and a two-stage cyclone set of the present invention;

(16) FIG. 11A is a CFD simulation showing velocity magnitude and stream for an embodiment of a two-stage stacked separator of the present invention;

(17) FIG. 11B is a CFD simulation showing out-of-page velocity component lines for an embodiment of a two-stage stacked separator of the present invention;

(18) FIG. 12A is a CFD simulation of a vertical cross-section at the first separation channel of an embodiment of a two-stage stacked separator of the present invention showing gas flow at the primary (i.e., first) stage;

(19) FIG. 12B is a CFD simulation of a vertical cross-section at the first separation channel of an embodiment of a two-stage stacked separator of the present invention showing gas flow at the secondary (i.e., upper) stage;

(20) FIG. 13A is CFD simulation of a two-stage stacked separator of the present invention showing predicted performance for removal of particles in the 10 to 100 micron diameter range at typical FCCU regenerator conditions;

(21) FIG. 13B is CFD simulation of a two-stage stacked separator of the present invention showing predicted performance for removal of particles in the >0 to 10 micron diameter range at typical FCCU regenerator conditions;

(22) FIG. 14 is line graph showing grade efficiency curve predictions for a two-stage stacked separator of the present invention at typical FCCU regenerator conditions;

(23) FIG. 15A is a side view of an embodiment of a third-stage separator (TSS) in accordance with the present disclosure;

(24) FIG. 15B is a cut-away view of the TSS of FIG. 15A;

(25) FIG. 15C is an enlarged close-up view of the peripheral channel exterior showing the solids ejection port; and

(26) FIG. 16 is line graph showing grade efficiency curve prediction for an embodiment of a TSS of the present invention at typical FCCU regenerator operating conditions.

DETAILED DESCRIPTION OF THE INVENTION

(27) While the disclosed uniflow cyclone separator invention is susceptible of embodiments in many different forms, there is shown in the appended drawings and will herein be described in detail at least one preferred embodiment of the invention with the understanding that the present disclosure is to be considered as an exemplification of the principles of the invention and is not intended to limit the broad aspect of the invention to any of the specific embodiments illustrated. Features and alterations described and/or illustrated for one specific embodiment may be applicable to other embodiments, even though not explicitly stated, as would be understood by a person of skill in the art.

(28) Single-Stage Cyclone

(29) A simple form of the invention is shown in FIGS. 6A-6C. This cyclone 10 differs from other uniflow cyclones because the vane hub 30 extends thru the entire collection zone 14 of the cyclone 10. The vane 24 initiates a vortex causing entrained dust particles to flow to the cyclone barrel wall 16. Dust particles flow to the wall 16 according to the theoretical principles discussed earlier. When the vortex reaches the top of the barrel 12 the particles are removed from the vortex by an enlarged section of the barrel 12 which creates a channel 18 for the particles to flow in. The gas vortex and any particles which do not reach the wall 16 continue into the top of the cyclone 10 and then out the top. The particles that collect in the channel 18 continue to rotate around the channel perimeter until they reach the solids ejection port 20 that connects the channel 18 to a dust hopper 22. At that point the particles are swept into the dust hopper 22 and eventually into a dip leg (not shown here) and either returned to a bed below in the case a fluidized bed or to an appropriate receptacle.

(30) FIG. 7 shows a cutaway of the outside wall of the channel 18. The wall has been cutaway so the shape of the channel 18 through which the solids exit the cyclone 10 can be shown. This invention is unique because it removes the particles from the vortex instead of removing the vortex from the particles.

(31) Two-Stage/Multi-Stage Cyclone

(32) Another unique feature of the disclosed cyclone 10 is that stages can be stacked one upon another without changing vortex direction. FIG. 8 illustrates a two-stage cyclone separator 110 having a first stage 100 and a second stage 200. This cyclone 110 is created by extending the barrel 12 and the center-pipe 26 of the single-stage cyclone 10, then adding a second vane 124 to the center-pipe 26 above the first collection channel 18. A second collection channel 118 is located at the appropriate elevation with a second dust hopper 122 and second solids ejection port 120. The second vane 124 would preferably have a different pitch so as to accelerate the gas to a desired velocity for the second stage 200.

(33) FIG. 8 shows the simplest form of a two-stage version of the cyclone 110. As described, the two-stage cyclone 110, or for that matter multiple stage designs, are created by stacking each consecutive stage onto a previous stage, beginning with the first stage 100. This has several advantages over the classic two cyclone, two-stage or multiple-stage designs.

(34) First, the vortex created in the disclosed design of FIG. 8 is continuous from stage to stage with only a minor modification at the second stage vane 124. This means that if a particle has traveled 75% of the way to the wall in stage one 100, it is still 75% of the way to the wall upon entering the second stage 200. Conversely, in a classic cyclone pair, the particle would be redistributed at the inlet losing any advantage gained in a previous stage.

(35) Second, the disclosed cyclone 110 induces a major direction change and gas acceleration at the inlet 40 to the device and then has a minor modification and small acceleration at the second vane 124. The classic cyclone has a similar major direction change and acceleration at the inlet, with a subtle direction change between the primary and secondary vortices, then a major acceleration into the outlet tube, followed by a major direction change and velocity change entering the second stage. The second stage of the classic cyclone has a further pressure drop as the gas flows from the primary to the secondary vortex, then to the outlet tube before exiting.

(36) Third, in a classic cyclone the gas enters between the top of the cyclone and about halfway down the barrel through an inlet duct. That means gas entering at the top of the cyclone has approximately two revolutions in the barrel while gas entering at the bottom of the inlet duct has only about one revolution. In the disclosed cyclone 10, 110, all of the gas enters the barrel 12 at the same approximate elevation. As a result, all of the gas undergoes the same number of rotations. If the barrels are of equal length (classic vs. present design), then the disclosed uniflow cyclone 10, 110 will have a longer effective barrel length and thus a higher potential efficiency than its classic counterpart. Likewise, a designer could decide to build a shorter cyclone barrel, for example about 75% of conventional barrel length, for an efficiency similar to the longer barreled classic design.

(37) Fourth, the disclosed cyclone 110 has a smaller footprint than the conventional voluted cyclone pair with the same gas capacity and barrel diameter. FIG. 9 shows a top view of an embodiment of numerous disclosed cyclone 110 laid out in a 42.5 ft diameter vessel 50. It shows 27 cyclone sets in the vessel. Compare this to FIG. 4 which shows the same 42.5 ft diameter vessel 50 with only 17 conventional cyclone pairs.

(38) While the disclosed cyclone 10, 110 can be used to increase the gas handling capacity of the vessel 50 beyond what is possible with conventional cyclones, it may not be practical to go that far. The superficial gas velocity will go up by the ratio of the number of cyclones, and that has a dramatic effect on the disengaging height. However, this capability to put more cyclones in the regenerator coupled with the higher efficiency of the cyclones could be used to reduce cyclone inlet velocity and prolong cyclone life.

(39) Fifth, the stacked pair of cyclones 110 has similar elevation requirements as conventional cyclones with the same gas capacity. FIG. 10 shows a comparison of a classic cyclone and an embodiment of the disclosed cyclone 110. Both have the same barrel diameter and gas capacity. The center pipe 126 of the disclosed cyclone 110 is the same diameter as a primary cyclone outlet tube, so they both have the same peak gas velocity. Both would be mounted under a plenum chamber at the top of the containment vessel 50. The center pipe 126 of the disclosed cyclone 110 can extend into the plenum chamber.

(40) The barrel 112 above the second particle collection channel 118 would be welded to the plenum chamber. The classic cyclone second stage outlet tube is also typically welded to the plenum chamber. The overall height of the two devices is very similar, approximately 210.5 inches for the classic cyclone and approximately 181 inches for a preferred embodiment of the disclosed cyclone. If credit is taken for the superior vortex length of cyclone 110, this design could be shortened by approximately 36 inches to give equivalent primary vortex lengths.

(41) Containment vessel tangent length is determined by one of two factors; either the necessary dip leg length to overcome cyclone pressure drop or the disengaging height. The “disengaging height” is the elevation at which the particle entrainment rate has stabilized. The disclosed cyclone 110 would seem to have a shorter disengaging height than the classic cyclone shown in FIG. 10. That is, the disclosed cyclone 110 has an inlet 40 at the bottom of the cyclone, whereas the classic cyclone has an inlet somewhat higher. However, while the disengaging height assumes a constant velocity, significant acceleration occurs when the rising gases encounter the bottom of a cyclone. This makes it more difficult to disengage additional amounts of particulate matter above the bottom of the primary dust hopper.

(42) Additionally, the stacked cyclone described herein would have longer dip leg clearances, which would reduce tangent length in cases where the dip leg length is controlling.

(43) FIG. 11 shows CFD analysis of tangential gas flow in a two-stage design with higher velocity in the second stage. This simulation shows a gas vent 52 from each of the dust hoppers and the analysis shows that the vent is not needed. It also shows an outlet vane 54 which is included to add stability to the center pipe 126. Especially notable in the simulation is the uniformity of the vortex streamlines and velocity profiles.

(44) In FIGS. 12A and 12B, the gas flow patterns in the cyclone, the solids separation channel, the solids extraction ports 20, 120, and the dust hoppers 22, 122 are shown. It is notable that the gas flow is very stable in the barrel area or collection zone 14 and the solids ejection ports 20, 120 have little effect on the gas flow patterns.

(45) FIGS. 13A and 13B show CFD model predictions for the removal of particles consistent with FCC catalyst at conditions similar to operating conditions typical of an FCC regenerator. The CFD modeling shows relative concentrations of particles and their typical flow paths in the cyclones. Since the concentration of the finer particles is small compared to overall quantities, the representations shown are more qualitative than quantitative. Therefore, it is very difficult to predict the collection efficiency for any particular size.

(46) FIG. 14 shows the predicted theoretical performance of an embodiment of a two-stage cyclone pair 110 from the theory developed earlier. As noted earlier, the theory derived from Stoke's Law does not take into consideration the interaction between larger particles and smaller particles in the centrifugal field. It represents the best efficiency one might expect from a perfect cyclone with very low dust loadings. As the dust loading is increased the efficiency curves, especially for the first stage, would be expected to shift to the left. The bulk of the particles feeding an FCCU cyclone would be much larger, with an average size of approximately 60 microns. The prediction says the first stage removes 100% of the particles greater than 24 microns and the second stage removes nearly 100% of the 16 micron and larger particles.

(47) 3.sup.rd Stage Separator

(48) The disclosed cyclone 10 can be used on third-stage separators, as well. The third-stage separator (TSS) is located downstream of a FCCU regenerator and was originally developed to remove any 10 micron and larger particles from a flue gas upstream of power recovery turbines. The ten microns plus (10+) particles cause considerable wear on turbine blades. More recently, the efficiency of the TSS has improved such that they are sometimes employed as air pollution devices and can be designed to remove four-plus (4+) micron particles and even smaller. As air pollution regulations become more restrictive, use of a TSS becomes less viable as final flue gas clean-up devices.

(49) These devices are somewhat smaller than those used in the regenerator with barrels sized in the 10 to 12 inch diameter range. Cyclones used in regenerators are normally sized between 50 and 60 inches in diameter. Because the particle loading to the TSS is much lower than in the regenerator (approx. 400 mg/Nm.sup.3 vs. approx. 0.7 lbs/ft.sup.3), they can be operated at much higher velocities, generally around 250 ft/sec.

(50) FIGS. 15A-15C show an embodiment of the disclosed cyclone 210 designed for TSS applications. This cyclone 210 would be substituted for the cyclones shown in FIG. 5. The flow is into the top of the cyclone 210 which is above the top tube sheet. The gas encounters the vane 224, and the vortex is formed. The particles migrate toward the wall 216 by centrifugal forces generated by the vortex and eventually into the enlarged section of the barrel 212 where they accumulate in the channel 218 until they are discharged from the port 220 shown in FIG. 15A. This channel 218 and solids ejection port 220 are located between the two tube sheets shown in FIG. 5 and flow out the bottom of the of that zone. The gas continues in a vortex to the bottom end of the cyclone 210 which discharges below the bottom tube sheet of FIG. 5. While a rather simple vane is shown here, the vane shown in FIG. 5 could also be used, or any other vane that produces desired vortex properties.

(51) An embodiment of the overall cyclone 210 is shown in FIG. 15A. Half of the barrel 212 has been removed in FIG. 15B to show the vane 224 and its relation to the solids collection channel 218 and the solids ejection port 220. FIG. 15C is a close up of the solids collection channel 218 from FIG. 15A including the solids ejection port 220. In some cases, the port will be extended even farther to ensure tangential flow from the cyclone channel.

(52) FIG. 16 shows the expected performance of the invention when it is operated at conditions consistent with FCCU Regenerator flue gas conditions. The design would be for a 10-inch barrel and two revolutions of the vortex. The designer can vary the performance by manipulating Equation 3 above. However, the higher the velocity, the greater the catalyst attrition, the greater the number vortex revolutions, the greater the catalyst attrition, and finally the narrower the gap (w.sub.c), the lower the cyclone capacity.

(53) The matter set forth in the foregoing description and accompanying drawings is offered by way of illustration only and not as a limitation. While particular embodiments have been shown and described, it will be apparent to those skilled in the art that changes and modifications may be made without departing from the broader aspects of applicants' contribution. The actual scope of the protection sought is intended to be defined in the following claims when viewed in their proper perspective based on the prior art.