Catalyst control and recovery valve with hermetic shutoff capability

Abstract

A slide valve having a valve disc slidably movable between a fully retracted, fully open position and a fully extended, sealed, fully closed position by an actuation stem, the actuation stem being flexibly coupled to the valve disc, the valve disc being selectively adjustable between a fully extended, sealed, fully closed position and a partially retracted, non-sealed, fully closed position to prevent the valve disc from binding in the fully extended, sealed, fully closed position.

Description

[Technical field]

[0001]

[0001] This application claims priority under 35 U.S.C. §119(e) to U.S. Provisional Patent Application No. 63 / 012,571, filed April 20, 2020, the entirety of which is expressly incorporated herein by reference.

[0002]

[0002] This disclosure relates to valves, and in particular to slide gate valves. More particularly, this disclosure relates to slide gate valves used in service for catalyst control and for catalyst withdrawal valves to control the flow of gas and catalyst material in fluid catalytic cracking processes. [Background technology]

[0003] Fluidized catalytic cracking is a process used in petroleum refineries to convert the high boiling, high molecular weight hydrocarbon fractions of petroleum crude oil into more useful gasoline, olefinic gases, and other products. The feedstock for the fluidized catalytic cracking process is typically a portion of crude oil having an initial boiling point above 340°C (644°F) at atmospheric pressure and an average molecular weight ranging from about 200 to 600 or more. The feedstock is heated to high temperatures and moderate pressures and contacted with a hot powdered catalyst.

[0004]

[0004] The catalyst breaks the long chain molecules of the high boiling point hydrocarbon liquid into shorter molecules that are collected as vapor. The heated feedstock is injected into a catalyst riser where it contacts and mixes with very hot powdered catalyst provided by a catalyst regenerator, vaporizing and cracking it into smaller vapor molecules. The catalyst flows into a reactor having a vessel where the cracked product vapor is separated from the spent catalyst, and the spent catalyst is returned to the catalyst regenerator vessel through a spent catalyst flow line. The flow of regenerated catalyst to the reactor is regulated by a regenerated catalyst flow line and a riser section. Three slide valves primarily control this catalyst flow between the regenerator and the reactor vessel (usually referred to as the Rx Catalyst valve, the spent catalyst valve, and the regenerated catalyst valve). There are two other valves used to control the catalyst from the regenerator in a flow scheme back to the regenerator, these are called Recirculation valves and Cooled Catalyst valves. These applications are found in Fluid Cokers, Flexicokers, FCCUs, RFCCUs, DCCUs, DCUs, and other similar types of refining processes that utilize refractory lined slide valves to control particulate flowing applications at high temperatures, to name a few.

[0005]

[0005] With the passage of time and with the deterioration of the catalyst particles, the reactivity of the catalyst is continually lost. This loss of reactivity must be rectified over time in the fluid catalytic cracking process by removing the catalyst from the regenerator and loading new catalyst into the regenerator. Both of these processes require the use of special slide gate valves that do not wear out when the catalyst impacts the internal surfaces during operation.

[0006] The catalyst comprises fines or particles having a particle size distribution ranging from about 5 microns to about 40 microns in size. The catalyst may comprise a crystalline zeolite, a matrix, a binder, and a filler component. The matrix component may comprise an alumina matrix component. The binder may be a silica sol and the filler may be a clay such as kaolin.

[0007]

[0007] Slide gate valves used in regenerated catalyst, spent catalyst, Rx catalyst, recirculated cooled catalyst service, or for catalyst recovery valve service, face problems in function and operation due to several factors. Slide gate valves for catalyst control and recovery applications must operate over a very wide range of temperature conditions, ranging from ambient temperature conditions that can be as low as -34°C (approximately minus 30°F), to operating temperatures of 1350°F or higher at the moment the valve is opened or even partially opened, i.e., used, to control catalyst flow. The flow of hot catalyst through the valve thermally shocks the valve, causing failure of wear-resistant surfaces and components of the valve.

[0008]

[0008] The flow of hot catalyst through the valve is also very harsh on the valve body, guides, orifice plate, actuation stem, and disk of the valve. The temperature fluctuations between the momentary heating at the initiation of catalyst flow and the cooling of the valve after catalyst flow is stopped place great stress on all components of the slide valve. This extreme set of temperatures relative to operating conditions results in premature failure of the slide valve.

[0009]

[0009] Also, the flow of catalyst through the slide valve is highly erosive, causing wear of the slide valve and its components. Even if the catalyst particle size is small, the flowing catalyst will "sand blast" any surface it comes into contact with, but at a significantly higher rate than regular cube-type silica sand particles. The flow of catalyst through the valve is driven by the pressure difference between the pressure upstream of the valve and the pressure seen downstream of the valve. This can be found in spent, regenerated, Rx, catalyst cooler, and recycle service, with pressures of up to 20 pounds per square inch gauge (psig). In the case of catalyst recovery valve service, the valve is connected to the bottom of the regenerator, whose pressure can be as much as 45 pounds per square inch gauge (psig) or more, and this pressure is applied downstream of the valve where partial and full vacuum exists. The pressure drop across the catalyst recovery valve is too great to withstand this type of valve. Normal operation of slide valves is typically maintained at less than 83 kPa (12 pounds per square inch) differential pressure during flow operation, and rarely operates at 103 kPa (15 to 20 pounds per square inch) differential pressure across the valve. Slide valves used as catalyst recovery valves may experience as much as 276 kPa (40 pounds per square inch) or 310 kPa (45 pounds per square inch) pressure drop across the valve.

[0010]

[0010] An additional problem that may be faced with a catalyst recovery valve occurs when there is bidirectional flow through the valve. In such operation, catalyst is initially loaded into the regenerator at the start of the process through the catalyst recovery valve, resulting in catalyst flow in the opposite direction to what would be considered normal flow. In such operation, the internal components of the valve must be designed for catalyst flow in both directions relative to the valve, with erosion and wear protection provided for the valve components in both directions of flow.

[0011] Another problem faced by conventional slide valves is that the valve actuating stem, which moves the valve disc between the open and closed positions, tends to bend when a force is applied by the actuating stem against the valve disc to move the valve disc to the closed position. The bending of the actuating stem can cause premature failure of the packing in the actuating stem stuffing box and cause the disc to become uncontrollable at the end of the stroke position. In addition, interference with catalyst buildup inside the valve can cause the disc to hit a mechanical stop at the end of the valve disc's closing stroke, sometimes before it reaches its fully closed position. Summary of the Invention [Means for solving the problem]

[0012]

[0012] In accordance with the present disclosure, a slide valve has a valve disc and a disc receiver having a disc guide and an orifice plate having an orifice, the disc valve being selectively slidable within the disc guide between a fully retracted fully open position allowing gas and particle flow through the orifice and a fully extended fully closed tight shutoff position sealing the orifice and preventing gas and particle flow through the orifice.

[0013] In an exemplary embodiment, the valve disc and disc receiver have separate angled wedges that engage one another in a wedge fashion to urge the valve disc into engagement with the orifice plate when the valve disc is in a fully extended, sealed, fully closed position, and the valve disc is selectively adjusted between a fully extended, sealed, fully closed position and a partially retracted, non-sealing, non-sealing position in which a small gap is formed between the valve disc and the orifice plate that allows gas to flow out of the orifice and through the gap between the valve disc and the orifice plate while preventing particles from flowing out of the orifice and through the gap.

[0014] In an exemplary embodiment, an actuation stem is coupled at a first end to a hydraulic cylinder (actuator) or a motorized drive assembly (actuator) and at a second end to a valve disc. The actuator is adapted to selectively linearly slide the actuator stem and valve disc between a fully retracted fully open position, a fully extended sealed shut fully closed position, and a partially retracted unsealed shut position. The second end of the actuation stem is flexibly coupled to the valve disc such that the valve disc is movable relative to the second end of the actuation stem such that the disc valve does not apply a bending force to the actuation stem when the valve disc is moved by the actuator.

[0015]

[0015] Additional features of the present disclosure will become apparent to those skilled in the art upon consideration of the exemplary embodiments which illustrate the currently recognized best modes of carrying out the present disclosure.

[0016] The detailed description makes particular reference to the accompanying drawings, in which: [Brief description of the drawings]

[0016] [Figure 1]

[0017] FIG. 2 is a front perspective view showing a slide valve and illustrating the direction of catalyst flow into and out of the valve during normal flow operation when used in a catalyst recovery process in accordance with the present disclosure. [Diagram 2]

[0018] FIG. 2 is a partially exploded front view showing the slide valve of FIG. [Diagram 3]

[0019] FIG. 2 is a partially exploded rear view showing the slide valve of FIG. [Figure 4]

[0020] FIG. 1 is a front perspective view of a gate assembly of a slide valve showing a valve disc receiver and an actuation stem for selectively sliding the valve disc relative to the valve disc receiver between a fully retracted, fully open position and a fully extended, fully closed, sealed shut position. [Diagram 5]

[0021] 5 is a front exploded view of the gate assembly of FIG. 4, additionally showing a valve disc movably coupled to a distal end of the actuation stem. [Figure 6]

[0022] FIG. 2 is a rear perspective view showing the gate assembly. [Figure 7]

[0023] FIG. 2 is a rear exploded view showing the gate assembly. [Figure 8]

[0024] 8 is a cross-sectional view taken along line 8-8 of FIG. 1 showing the slide valve, showing the valve disc in a fully closed position, fully extended and sealed shut, relative to the disc-receiving orifice plate. [Figure 9]

[0025] 9 is a detail view taken along line 9 in FIG. 8 showing the disk in a fully extended, hermetic shutoff, fully closed position. [Figure 10]

[0026] 10 is a detailed view taken along line 10 of FIG. 9 showing the disk in a fully extended, hermetic shutoff, fully closed position. [Figure 11]

[0027] 9 is a cross-sectional view of a slide valve similar to that of FIG. 8 but showing the valve disc partially retracted relative to the orifice plate from a fully closed, sealed shut position at fully extended, to a partially retracted, non-sealed shut position. [Figure 12]

[0028] 12 is a detailed view taken along line 12 in FIG. 11 showing the valve disc spaced a short distance from the orifice plate when the valve disc is in a partially retracted, non-sealing shut-off position resulting in a small gap between the valve disc and the orifice plate. [Figure 13]

[0029] 13 is a detailed view taken along line 13 in FIG. 12 showing the gap between the valve disc and the orifice plate when the valve disc is in a partially retracted, non-sealing shutoff position. [Figure 14]

[0030] FIG. 2 is a cross-sectional view showing the valve in a fully open position with the valve disc fully retracted relative to the orifice plate to allow catalyst to flow through the valve. [Figure 15]

[0031] 1 is a graph of time and actuator force applied to a valve disc showing actuator force applied to a valve disc of a valve versus time and further showing the position of the valve disc relative to an orifice plate; [Figure 16]

[0032] FIG. 2 is a perspective view of a valve disc. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0017]

[0033] A valve 10, such as a slide valve, according to the present disclosure is shown in Figures 1-14. Valve 10 may include a catalyst recovery valve when used in connection with fluid catalytic cracking and other processes to control the flow of particles such as catalyst. Valve 10 has a body 12 and an elongated housing 14 having a first end 16 and a second end 18 coupled to the housing 14. An actuator 20 is coupled to the second end 18 of the housing 14.

[0018]

[0034] The valve 10, as shown in Figures 4-7, has a gate assembly 90. The gate assembly 90 has an orifice plate 92, a valve disc 166 actuated by an actuator 20, and a pair of valve body guides 136a, 136b that enable the bubble disc 166 to move relative to the orifice plate 92 from a first closed position where the valve disc 166 blocks the orifice 144, as shown in Figure 8, to a second open position where the valve disc 166 is disengaged from blocking the orifice 144, as shown in Figure 14, to allow gas and particle flow through the orifice 114.

[0019]

[0035] As the actuator 20 slides the actuation stem 196 and valve disc 166 from a fully open position with the disc 166 fully retracted, as shown in Figure 14, toward a fully closed position with the disc 166 fully extended, as shown in Figure 8, the wedge surface 162 of the wedge 160 engages the wedge surfaces 186 of the wedges 184A-B of the disc 166. The wedge surface 162 of the wedge 160 presses in a wedge manner against the top surface 172 of the disc 166 in an orientation generally transverse to the axis 180 and generally parallel to the central axis 62 into sealing engagement with the sealing surface 128 of the orifice plate 92 and ring 126. The disk 166 thereby tightly and completely seals the orifice 114 and the inlet passage 56 of the inlet 48 and the outlet passage 70 of the outlet 50 from the chamber 38 of the body 12, preventing gas flow and particle flow in the gas-solids mixture from passing through the orifice 114 into the chamber 38 and the outlet passage 70.

[0020]

[0036] To prevent the disc 166 from getting stuck in the fully extended, sealed shut, fully closed position shown in Figures 8-10, the valve disc 166 may be periodically adjusted or slidably moved between the fully extended, sealed shut, fully closed position and the slightly partially retracted, non-sealed shut position shown in Figures 11-13. When the actuator 20 partially retracts the actuation stem 196 and disc 166 along the axis 180 to the partially retracted, non-sealed shut position shown in Figures 11-13, the disc 166 is moved a very short distance along the axis 180 and clears the side wall 32 of the body 12. This sliding movement of the valve disc 166 relative to the orifice plate 92 prevents the valve disc 166 from sticking to the orifice plate 92. Movement of the valve disc to a partially retracted, non-sealing shutoff position creates a small opening to allow some gas, but not particles, to pass through the orifice 114 due to the nominal size of the gap 171 between the disc 166 and the orifice plate 92.

[0021]

[0037] The body 12 of the valve 10 has a top portion 24, a bottom portion 26 spaced from the top portion 24, and a cylindrical sidewall 28. The sidewall 28 extends between opposing ends of the top portion 24 and the bottom portion 26. The top portion 24, the bottom portion 26, and the sidewall 28 together form an interior surface 34 and an exterior surface 36. The body 12 has a hollow interior chamber 38 defined therein by the top portion 24, the bottom portion 26, and the sidewall 28. The body 12 has a flange 30 formed with an opening 40. The opening 40 is configured to receive a valve cap 31. The valve cap 31 closes the opening 40 in the flange 30 and has a bracket assembly 33 that supports an actuator 20, which drives an actuation stem 196. The opening 40 is in fluid communication with the chamber 38. The top portion 24 of the valve 10 has a recessed pocket 42 formed in the interior surface 24 of the top portion 24 .

[0022]

[0038] The body 12 of the valve 10 has an inlet 48 in fluid communication with the chamber 38 and an outlet 50 in fluid communication with the chamber 38, as shown in FIG. 8. The inlet 48 has a tubular stem 52 connected to the top portion 24 and extending outwardly therefrom. An outwardly extending flange 54 may be connected to an outer end of the stem 52. The flange 54 may have a plurality of bolt holes arranged in a generally circular or generally rectangular bolt hole pattern about a central axis of the stem 52. The inlet 48 has a fluid inlet passage 56 extending through the top portion 24, the stem 66, and the flange 68. The inlet passage 56 is selectively fluidly connected to the chamber 38 of the body 12. The inlet passage 56 has a first port 58 formed in the interior surface 34. The inlet passage 56 has a second port 60 formed in the inlet 48. The first port 58 and the second port 60 are in fluid communication with each other. An inlet passage 56 extends along a central axis 62 between a first port 58 and a second port 60. The inlet passage 56 is defined by a generally cylindrical sidewall within the stem 52 that extends between the first port 58 and the second port 60.

[0023]

[0039] The outlet 50 has a tubular stem 66 coupled to and extending outwardly from the bottom portion 26 of the body 12. An outwardly extending flange 68 may be coupled to an outer end of the stem 66. The flange 68 may have a plurality of bolt holes arranged in a generally circular or generally rectangular bolt hole pattern. The outlet 50 has a fluid outlet passage 70 extending through the bottom portion 26, the stem 66, and the flange 68. The outlet passage 70 is in fluid communication with the chamber 38 of the body 12. The outlet passage 70 has a first port 72 formed in the interior surface 34 of the bottom portion 26 and a second port 74 formed in the outer end of the flange 68. The first port 72 and the second port 74 are in fluid communication with each other.

[0024]

[0040] An outlet passage 70 extends through the central axis 62 such that the inlet passage 56 and the outlet passage 70 are generally coaxially aligned with one another along the central axis 62. The outlet passage 70 may be defined by a generally cylindrical sidewall 76 extending inwardly from the second port 74. The outlet passage 70 may be defined by a generally conical sidewall 78 extending between the interior surface 34 of the bottom portion 26 and the cylindrical sidewall 76. The conical sidewall 78 tapers inwardly as it extends from the interior surface 34 of the bottom portion 26 toward the cylindrical sidewall 76. The body 12 of the valve 10 may be formed from a metallic material.

[0025]

[0041] The valve 10, as shown in Figures 4-7, has a gate assembly 90. The gate assembly 90 has a valve disc receiver 91 located within the chamber 38 of the body 12 and connected to the body 12. The valve disc receiver 91 has an orifice plate 92. The orifice plate 92 may be generally rectangular, as shown in Figure 5, having a generally flat top wall having a generally flat top surface 94 and a generally flat bottom wall having a bottom surface 96 spaced from and generally parallel to the top surface 94. The orifice plate 92 has a generally linear first end 98 and a linear second end 100 that are spaced apart and generally parallel. The orifice plate 92 has a first lateral edge 102 extending generally linearly between the first end 98 and the second end 100 of the orifice plate 92, and a second lateral edge 104 spaced from and generally parallel to the first lateral edge 102 and extending generally linearly between the first end 98 and the second end 100 of the orifice plate 92. The first lateral edge 102 and the second lateral edge 104 each have a seat member 106 extending from the top surface 94 of the orifice plate 92. The seat member 106 has a generally cylindrical side wall 108 forming a periphery of the seat member 106 adapted to seat and lie within the pocket 42 of the top portion 24 of the body 12, where an end wall 112 of the projection 108 is matingly sealingly engaged with a bottom wall of the pocket 42.

[0026]

[0042] The orifice plate 92 of the gate assembly 90 has an orifice 114 extending through the orifice plate 92 and the sheet member 106 that forms a fluid passageway through the orifice plate 92 and the sheet member 106. The orifice 114 has a first port 116 located in the end wall 112 of the sheet member 106 and a second port 118 located in the bottom surface 96 of the orifice plate 92. The orifice 114 has a sidewall 120 extending between the first port 116 and the second port 118, as shown in FIG. 7. The sidewall 120 and the area around the orifice 114 have a refractory liner 122. The refractory liner 122 is erosion resistant and provides insulation to limit damage to the orifice plate 92 caused by high temperatures and abrasive materials. The refractory material 122 is held in place by a retainer 123 positioned between the wear resistant liners 122. In effect, the refractory material 122 surrounds the orifices 114 of the orifice plate 92.

[0027]

[0043] The orifice plate 92 further includes a sealing member 126, as shown in FIG. 7. The sealing member 126 surrounds the orifice 114 and is positioned radially outward from the refractory material 122. The sealing member 126 is preferably formed from an erosion- and wear-resistant material, such as STELLITE alloy, available from Kennametal Inc. under the trademark STELLITE. STELLITE alloy is used on the sealing member 126 and the retainer 123 to limit erosion and wear. The refractory material 122 positioned between the orifice 114 and the sealing member 126 helps prevent hot gases and abrasive materials from wearing away the sealing member 126 when the disk 166 is opened. The wear-resistant liner 122 extends between the first port 116 and the second port 118. The sealing member 126 has a flat sealing surface 128 that is sealingly engaged with the valve disk 166. To provide a sealing surface that is very flat and smooth to prevent unwanted leakage, the sealing surface 128 may be ground smoothly to a typical RMS 32 finish.

[0028]

[0044] The receiver 91 of the gate assembly 90 is configured to further include a valve disc guide 136A and a valve disc guide 136B to form the receiver 91 within which the valve disc 166 slides from an open position to a closed position, as shown in Figures 6 and 7. The valve disc guides 136A-B are constructed substantially identically to one another, but are constructed to be mirror images of one another. Each valve disc guide 136A-B extends between a first end 138 and a second end 140. Each valve disc guide 136A-B has a generally planar inner wall 142 and spaced apart, generally parallel, planar outer walls 144, as shown in Figure 6. The inner wall 142 has a series of channels 143 formed therein to allow leaked catalyst material to fall from the valve disc guides 136A-B. Each valve body guide 136A-B has an elongated concave guide channel 146 extending from a first end 138 to a second end 140.

[0029]

[0045] Each guide channel 146 of the plug guides 136A-B has a generally planar sidewall 148 and a generally planar wall 150 extending between the first end 138 and the second end 140 of the plug guides 136A-B. The sidewall 148 of the guide channel 146 is generally parallel to the interior wall 142. The wall 150 of the guide channel 146 extends generally perpendicularly between the interior wall 142 and the sidewall 148 of the guide channel 146. Each plug guide 136A-B has a seat 152 extending generally linearly between the first end 138 and the second end 140. Each seat 152 of the plug guides 136A-B is adapted to receive and interlock with a respective seat 106 of the orifice plate 92. Disc guide 136A is coupled to first lateral edge 102 of orifice plate 92 and disc guide 136B is coupled to second lateral edge 104 of orifice plate 92 such that guide channels 146 of disc guides 136A-B are in opposing spaced apart relationship and extend generally parallel to one another. Guide discs 136A-B preferably have a layer of STELLITE alloy for improved wear and temperature resistance.

[0030]

[0046] Each of the valve body guides 136A-B has a wedge 160, as shown in FIG. 5. The wedge 160 can be located on the inner wall 142 of the valve body guides 136A-B and extends outwardly from the inner wall 142. Each of the wedges 160 has a generally flat inclined wedge surface 162. The wedge surface 162 is inclined, i.e., sloped, with respect to a plane including the wall 150 of the guide channel 146. The wedge surface 162 slopes toward the wall 150 of the guide channel 146. The wedge 160 is spaced from the second end 140 of the valve body guides 136A-B. The wedge 160 is closer to the second end 140 than the first end 138 of the valve body guides 136A-B. The wedge surface 162 is spaced from the bottom surface 96 of the orifice plate 92 and is located at a constant inclination angle with respect to the bottom surface 96 of the orifice plate 92.

[0031]

[0047] The wedges 160 of the plug guides 136A-B are positioned to allow linear movement of the disc 166 relative to the orifice plate 92 such that near the end of its travel it moves closer to and engages the seal member 126 to seal off the orifice 144. As the valve disc 166 engages the wedges 160, the valve disc 166 is raised and clears the wall 150 of the plug guides 136A-B. As the valve disc 166 is moved rearward from its fully closed position, the valve disc 166 begins to descend against the wedges, creating a gap between the valve disc 166 and the seal member 126, thereby preventing the undesired flow of catalyst material but allowing hot gases to exit the orifice 114.

[0032]

[0048] Each plug guide 136A-B may have a wear-resistant liner 164, which is a layer formed from a wear-resistant material, such as a Stellite alloy. The wear-resistant liner 164 may form the side walls 148 and walls 150 of the guide channel 146, the interior walls 142, the wedges 160 and the wedge faces 162 of each plug guide 136A-B. While the orifice plate 92 and plug guides 136A-B may generally be formed from a metallic material, the wear-resistant liner 164 may be formed from a metal, ceramic, or other wear-resistant material.

[0033]

[0049] The gate assembly 90 further includes a valve disc 166. The disc 166 may comprise a generally rectangular plate having a proximal end 168 and a spaced apart distal end 170. The disc 166 has a generally planar top surface 172 and a generally planar bottom surface 174 that is spaced apart and generally parallel to the top surface 172. The disc 166 has an elongated generally linear first lateral edge 176 and a spaced apart generally parallel elongated linear second lateral edge 178. The first lateral edge 176 of the disc 166 is adapted to be slidably received within and positioned within the guide channel 146 of the disc guide 136A of the receiver 91. The second lateral edge 178 of the disc 166 is adapted to be slidably received within and positioned within the guide channel 146 of the disc guide 136B of the receiver 91. A disk 166 is adapted to be selectively slidable within the guide channel 146 relative to the plug guides 136A-B and the orifice plate 92 of the receiver 91 along a generally linear axis 180 that is generally perpendicular to the central axis 62 .

[0034]

[0050] The disk 166 further has a first elongated groove 167 and a second elongated groove 169. The grooves 167 and 169 engage with and slide within the guide channel 146 of the valve disc guides 136A-B. The grooves 167 and 169 have a first wall 171 and a second wall 173 that is generally perpendicular to the first wall 171. The first walls 171 of the grooves 167, 169 slide along the wall 150 when the disk 166 is moved relative to the valve disc guides 136A-B.

[0035]

[0051] As shown in FIG. 7, the disk 166 has spaced apart wedges 182A and 184B extending upwardly from the first wall 171 of the grooves 167, 169. Each wedge 184A-B has a generally flat, sloping wedge surface 186. The wedge surfaces 186 of the wedges 184A-B are generally coplanar with one another. Each wedge surface 186 of the wedges 184A-B extends outwardly and slopes from the first wall 171 toward the bottom surface 174 of the disk 166. The wedges 184A-B are offset from the proximal end 168 of the disk 166. This location of the wedges 184A-B assists in uniformly raising the proximal end 168 and distal end 170 simultaneously as the disk 166 is moved from a partially open position to a fully closed position. A wedge surface 186 of the wedge 184A is adapted to slidably engage and mate with the wedge surface 162 of the wedge 160 of the disc guide 136A, thereby functioning as a cam to translate the linear motion of the valve disc 166 to move the valve disc 166 towards the orifice plate 92. A wedge surface 186 of the wedge 184B is adapted to slidably engage and mate with the wedge surface 162 of the wedge 160 of the disc guide 136B. When the disc 166 is moved from the open position to the closed position, the wedges 184A-B of the disc 166 are engaged with the wedges 160, 162 of the disc guides 136A-B. The slidable engagement of the wedges causes the linear motion of the disc 166 to also have a translational motion that is perpendicular to the linear motion.

[0036]

[0052] The top surface 172, the first and second lateral edges 176 and 178, the distal end 170, the grooves 167 and 169, and the wedge faces 186 of the wedges 184A-B can have wear-resistant covers made from a wear-resistant material, such as a STELLITE alloy. The proximal end 168 of the disk 166 has a connector 190. As shown in FIG. 5, the connector 190 can include a generally T-shaped slot 192 extending between the top surface 172 and the bottom surface 174. The T-shaped slot 192 has legs with proximal ends that form an opening in the proximal end 168 of the disk 166. The T-shaped slot 192 further has opposing recesses extending outward in opposite directions from the distal ends of the legs of the T-shaped slot 192. The slots 192 are designed to allow the disc 166 to move laterally and translate upward to create a seal when closing the disc 166 without applying undesirable side loads to the actuation stem 196 that could bend or otherwise damage the stem 196. While the disc 166 may be made from a metallic material, the wear-resistant cover layer may be formed from a metal, ceramic, or other wear-resistant material.

[0037]

[0053] The offset of the guides 136A-B on the solid / notched section is approximately 4.5 inches backset from the port opening 114. The offset of the guide inclined flats or wedges 160 from the opening of the port 114 is 3 inches. Normal wear or erosion of the guides on prior art valves usually occurs at the end of the guide under the overhanging portion of the orifice plate. The spray effect of material exiting the port 114 due to the pressure differential is now directed forward of where the wedges 160 are located in the present invention so that the erosion effect does not affect the overall performance of the wedges 160 of the guides 136A-B. The wedge 160 area is formed as part of the guides 136A-B and not a separate component. The disc 166 of the present design does not stick in the closed position due to the steeper inclined flats and due to the disc 166 being a single entity against the seat 126.

[0038]

[0054] The disk 166 preferably has 3 inches of refractory material 191 on the nose 197 where a pressure drop effect occurs as shown in FIG. 15. A STELLITE alloy retainer is positioned between the refractory material 191 to help retain the refractory material 191. The disk 166 further has a seat ring member 193 that fits over the seat 126 of the orifice plate 92 to form a seal with the seat 126 when the disk 166 is in the fully closed position. The seat ring member 193 is preferably made from STELLITE alloy and surrounds a central region 195 having the refractory material. The disk 166 preferably has 6.5 inches of overlap when the disk 166 is in the closed position, thereby providing higher shutoff functionality even if the seat ring member 193 cannot completely seal against the seat 126 of the orifice plate 92.

[0039]

[0055] The central region 195, nose 197, and lower leading edge 197 of the disk 166 are all rebuildable, meaning that the refractory material can be replaced with new refractory material after it has been damaged by heat and erosion. The seat ring member 193 of the disk 166 is arranged to provide a 360 degree surface that matches the same shaped (360) surface of the seat 126 of the orifice plate 92. The disk seating surface, inclined mating surfaces, and runners have a STELLITE alloy overlay to reduce wear caused by severe operating conditions. The seat 126 of the orifice plate 92 has the same shape as the seat ring member 193 and is arranged to contact together 1% short of the fully closed position of the disk 166 to allow for potential wear of the inclined flat surfaces.

[0040]

[0056] The seating surface 126 of the orifice plate 92 is backset 3 inches from the port edge where the pressure drop is. If the orifice plate 92 is made with raised ports so that there are any cutouts in the orifice plate 92 on the back side 99 (facing the open position), the refractory surface of the orifice plate will be eroded and the metal at the base of the orifice plate 92 will not be eroded, thereby allowing the orifice plate 92 to be completely rebuildable so that the refractory material can be replaced.

[0041]

[0057] Guides 136A-B are preferably made with wedges 160 as a solid, integral piece and are not welded or secured with fasteners. This provides maximum strength against the inclined plane. Guides 136A-B are "longer" at the long side 146 of the "L" shape, which provides more strength in the guide and in the area where the inclined plane is. Additionally, guides 136A-B are thicker at the short side 142 of the "L" shape, which provides more runner support against the guide. Guides 136A-B have notches 143 and also have a layer of STELLITE alloy for all wear surfaces.

[0042]

[0058] The disk 166 has an additional offset of 1.5 inches on the sides 176, 178 so that the seat ring member 193 has sufficient surface area available to make a seal. The refractory material of the orifice plate disk 166 around the edges is secured with retaining tabs. The refractory material located in the central area 195 is secured with a hexagonal mesh or hexagonal shaped retaining member to maintain its position. This creates a hexagonal pattern of refractory tiles in the central area 195. The orifice plate 92 and disk 166 being manufactured are marked during the machining process for the retaining tabs and hexagonal mesh to secure the refractory material so that the fabricator knows exactly where to place the retaining tabs and hexagonal mesh, thereby eliminating a lot of human input during the manufacturing stage. This arrangement ensures that all components are exactly as the engineer selected the design.

[0043]

[0059] The valve 10 has an elongated actuation stem 196 having a first end 198 and a second end 200, as shown, for example, in Figures 2 and 7. The actuation stem 196 is adapted to have the first end 198 coupled to the actuator 20. The second end 200 of the actuation stem 196 is adapted to be movably coupled to the proximal end 168 of the disk 166. The second end 200 of the actuation stem 196 has a connector, such as a generally T-shaped head 202, adapted to be loosely received and positioned within the T-shaped slot 192 of the disk 166, movably interlocking the disk 166 to the actuation stem 196. The actuation stem 196 extends along the axis 180 between the first end 198 and the second end 200. A T-shaped head 202 extends outwardly from the second end 200 transversely to the axis 180 and has opposed projections 201 adapted to be loosely received within opposed recesses of the T-shaped slot 192. An actuation stem 196 is adapted to be selectively linearly moved along the axis 180 by the actuator 20 toward or away from the actuator 20 along the axis 180. The T-shaped head 202 of the actuation stem 196 and the T-shaped slot 192 of the disk 166 form a flexibly movable and pivotable connection between the disk 166 and the actuation stem 196 such that the actuation stem 196 can selectively move the disk 166 relative to the receiver 91 as the actuation stem 196 moves generally linearly along the axis 180, while the disk 166 can pivot and translate laterally relative to the T-shaped head 202 of the actuation stem 196 such that the disk 166 can move into sealing engagement with the orifice plate 92 in the closed position. The second end 200 of the actuation stem 196 is not rigidly connected to the disk 166. Thus, the disk 166 does not exert a bending force on the actuation stem 196 as the actuation stem 196 slides the disk 166 sideways and upward along the wedge 160 of the guide members 136A-B. Other types of flexible connections between the actuation stem 196 and the disk 166 may also be utilized, such as, for example, a ball and socket or hinge pin.

[0044]

[0060] As shown in FIG. 8, the actuation stem 196 extends outwardly through the opening 40 in the body 12 and into the housing 14 through a packing ring 206 that extends closely around the actuation stem 196. The actuation stem 196 further slidably extends through a packing gland 208 that extends closely around the actuation stem 196. A first end 198 of the actuation stem 196 is coupled to an actuator 20. The actuator 20 may comprise a hydraulic cylinder or an electric actuator having an electric motor 210. The actuator 20 is adapted to selectively movably slide the actuation stem 196 and the disk 166 in a generally linear manner along an axis 180 relative to the body 12, the receiver 91, and the orifice plate 92 between a fully closed, fully extended, sealed shut position shown in FIG. 8 and a fully open, fully retracted position shown in FIG. 14. The housing 14 has a resilient coil spring 212 which resiliently biases the actuation stem 196 and the disk 166 along the axis 180 away from the actuator 20 and toward the side wall 32 of the body 12, and toward the fully extended, hermetically sealed, fully closed position.

[0045]

[0061] The inlet 48 of the body 12 is adapted to be placed in communication with a source of a hot gas-solids mixture. The gas-solids mixture may include a gas, such as air, and solid particles, such as catalyst. The gas-solids mixture is supplied to the inlet 48 under pressure. When the disk 166 is in the fully extended, fully closed, seal-off position shown in FIG. 11, the disk 166 tightly and completely seals the orifice 114 and the inlet passage 56 and outlet passage 70 from the chamber 38, thereby preventing the flow of gas and particles in the gas-solids mixture from the inlet passage 56 to the outlet passage 70.

[0046]

[0062] As the actuator 20 slides the actuating stem 196 and stem 166 from a fully open position with the disk 166 fully retracted toward a fully closed position with the disk 166 fully extended, the wedge surfaces 162 of the wedges 160 of the receiver 91 are engaged with the wedge surfaces 186 of the wedges 184A-B of the disk 166, respectively. The wedge surfaces 162 of the wedges 160 act as cams to wedge the disk 166 in a direction generally transverse to the axis 180 and generally parallel to the central axis 62 into sealing engagement with the orifice plate 92 and sealing surface 128 of the ring 126. The disk 166 thereby tightly and completely seals the orifice 144 and the inlet passage 56 of the inlet 48 and the outlet passage 70 of the outlet 50 from the chamber 38 of the body 12, preventing the flow of gas and particles in the gas-solids mixture through the orifice 114 into the chamber 38 and the outlet passage 70.

[0047]

[0063] When manufacturing the valve 10, various inclinations for the wedges will be used and will vary depending on the specific function or size of the valve. The inclination of the wedges may range from about 9 degrees to about 20 degrees, and preferably from about 10 degrees to about 15 degrees. An inclination of less than 8 degrees could potentially cause the valve disc 166 to lock or stick in the closed position, making it difficult to open under normal operation of the valve 10. The weight of the valve disc 116 and the flow through the orifice 114 allow the wedges to remain in contact as the valve disc 166 is moved from the closed position toward the open position.

[0048]

[0064] When it is desired to allow the gas-solids mixture to flow from the inlet passage 56 to the chamber 38 and the outlet passage 70 and thus through the valve 10, the actuator 20 slidably retracts the actuation stem 196 and the disc 166 along the axis 180 to a fully retracted, fully open position shown in FIG. 14. As shown in FIG. 14, the disc 166 is slid along the axis 180 relative to the orifice plate 92 and away from the side wall 32 of the body 12 such that the disc 166 does not cover any portion of the orifice 114 in the orifice plate 92. When the disc 166 is in the fully retracted, fully open position shown in FIG. 14, the gas-solids mixture is allowed to flow from the inlet passage 56, through the orifice 114 in the orifice plate 92, through the chamber 38 of the body 12, through the outlet passage 70 of the outlet 50 and thereby outwardly from the valve 10.

[0049]

[0065] The valve 10 is used to control the flow of gas, liquid, and catalyst material in a fluid catalytic cracking process. The valve 10 has a valve body 12 configured with an interior chamber 34. The valve body 12 has an inlet 48 and an outlet 50. The valve 10 has an orifice plate 92 positioned within the chamber 34. The orifice plate 92 is formed with an orifice 114. The valve 10 further has a disc guide 136 positioned proximate to the orifice 114. The disc guide 136 has a guide channel 146. The disc guide may be a single piece unit, a multi-piece unit, part of the orifice plate 92, or part of the valve body 12. The valve 10 further includes a valve disc 166 configured to slide along the guide channel 146 from a fully open position, where gas, liquid, and catalytic material can pass through the orifice 114, to a fully closed position, where the orifice 114 is blocked, thereby preventing the flow of gas, liquid, or catalytic material through the orifice 114. The valve further includes a cam located within the interior chamber 34 of the valve body 12. The cam may be in the form of a wedge 160, a wedge 184, or some other cam or inclined flat surface located within the valve body or on the orifice plate. Movement of the valve disc 166 from the fully open position to the fully closed position causes the valve disc 166 to slide linearly along the guide channel 146 until a point in the movement of the valve disc 166 at which point the cam translates the valve disc 166 toward the orifice plate 92, thereby sealing the valve disc 166 against the orifice plate 92 to block flow through the orifice 114.

[0050]

[0066] 8-10, disc 166 may potentially become stuck in this position, making it difficult, if not impossible, to move disc 166 to its fully retracted, fully open position due to the wedging forces exerted by wedges 160 and 184A-B as they press disc 166 against orifice plate 92. Disc 166 may potentially become stuck further due to particles in the gas-solid mixture that may become positioned between wedge surface 162 of wedge 160 and wedge surface 186 of wedges 184A-B and between top surface 172 of disc 166 and orifice plate 92, which may become sticky due to heating, thereby causing the individual mating surfaces to adhere to one another.

[0051]

[0067] To prevent the disk 166 from getting stuck in the fully extended, sealed, fully closed position shown in Figures 8-10, the disk 166 may be periodically adjusted or slidably moved between the fully extended, sealed, fully closed position and the slightly partially retracted, non-sealing, blocked position shown in Figures 11-13. When the actuator 20 partially retracts the actuation stem 196 and the disk 166 along the axis 180 to the partially retracted, non-sealing, blocked position shown in Figures 11-13, the disk 166 is moved a very short distance along the axis 180 and clears the side wall 32 of the body 12, so that the top surface 172 of the disk 166 is no longer pressed into tight sealing engagement with the orifice plate 92, but is spaced a short distance from the orifice plate 92, thereby creating a short gap 216 between the top surface 172 of the disk 166 and the orifice plate 92. The width of the gap 216 may be less than the minimum particle size of the particles in the gas-particle mixture. The gap 216 may allow a small amount of gas in the solid-gas mixture in the orifice 114 of the orifice plate 92 to flow through the gap 216 into the chamber 38 of the body 12 and into the exit passage 70 of the outlet 50, but the gap 216 is small enough to prevent particles in the gas-particle mixture in the orifice 114 of the orifice plate 92 from passing through the gap 216 into the chamber 38. Thus, when the disk 166 is in the partially retracted non-sealing blocking position, the disk 166 prevents the flow of particles in the gas-particle mixture in the inlet passage 56 and the orifice 114 from flowing through the orifice 114 into the chamber 38 of the body 12 and into the exit passage 70 of the outlet 50, thereby maintaining a blocking state of the flow of particles in the gas-particle mixture.

[0052]

[0068] The adjustment or cycling of the disk 166 between the fully extended, sealed, shut-off, fully closed position shown in Figure 8 and the partially retracted, non-sealing, shut-off position shown in Figure 11 prevents the disk 166 from getting stuck in the fully extended, sealed, shut-off, fully closed position. Figure 15 is a graph of the force applied to the disk 166 by the actuator 20 versus time illustrating the movement of the disk 166 between the fully retracted, fully open position and the fully extended, sealed, shut-off, fully closed position, as well as the adjustment of the disk 166 between the fully extended, sealed, shut-off, fully closed position and the partially retracted, non-sealing, shut-off position.

[0053]

[0069] The actuator 20 is adapted to control the magnitude of the linear thrust applied by the actuator 20 to the actuation stem 196 to be plus or minus about 1 pound of force from the desired thrust. The thrust force that the actuator 20 exerts to seal the disk 166 in a fully extended, sealed, fully closed position can be controlled to be about 5% to 10% of the total force available from the actuator 20. The actuator 20 can provide a retracting pulling force to the actuation stem 196 and disk 166 that is about 30% of the total force available from the actuator 20.

[0054]

[0070] The actuator 20 moves the disk 166 to a desired position, by measuring the position of the disk 166, toward the fully extended, sealed, closed position, and then may slightly retract the disk 166 by up to about 0.5% of the travel, and then extend the disk 166 to the fully extended, sealed, closed position with the desired thrust. This allows the actuator stem 196 to readjust itself with the disk 166 to eliminate any bending in the actuator stem 196 as the disk 166 is driven to the fully extended, sealed, closed position. The actuator 20 will then selectively adjust the disk 166 between the fully extended, sealed, closed position and the partially retracted, unsealed, closed position by about 0.5% of the travel, and the retraction force required to move the disk 166 to the partially retracted, unsealed, closed position is monitored. As long as the retraction force remains below a selected magnitude, the valve 10 is deemed to be operating normally. If the disk 166 becomes stuck or sticky within the opening, resulting in a greater retraction force being required to retract the disk 166, the closing force applied to the disk 166 will be reduced by approximately 2%. Additionally, the magnitude of the retraction force applied to the disk 166 may be increased by approximately 5%. The disk 166 will remain reliably movable when desired.

[0055]

[0071] An actuator 20 can be programmed to selectively open and close the valve based on programmed criteria to control the amount of hot catalyst from the regenerator that flows through the valve 10. Tens of tons of catalyst per day or week can be calculated and controlled to flow through the valve 10. Controlling the catalyst flow allows for control of the piping temperature downstream of the valve 10.

[0056]

[0072] In the unlikely event that the disc could potentially stick in the seated position, the fluid circuit is designed to reduce the amount of force that would seat the valve disc 166 when emergency "closing" the valve disc 166. The fluid circuit functions to emergency close the valve in the presence of a power drop or a signal provided from the command center of the refinery FCCU. When an emergency command is given, the fluid system releases fluid from the accumulator (hydraulic piston type) directly to the rear port of the cylinder, driving the valve disc 166 to the closed position.

[0057]

[0073] Since the valve disc 166 operates upon power loss and is considered a fail-safe mechanism, no electricity is required to move the valve disc 166 to the closed position. Since the emergency shutoff system operates without available electricity, there is no way to "control" the amount of force applied to the disc in a normal ESD circuit. The fluid circuit has a hydraulic fluid reducing valve to control the fluid pressure moved from the accumulator to the cylinder during the emergency shutoff function. The control circuit controls the amount of force applied to the valve disc 166 and is adjustable for use in future applications of various size valves and various loads controlled in the closed direction.

[0058]

[0074] While the adjustment or cycling of the disc 166 is optional, testing has shown that undesired sticking of the valve disc 166 does not occur as predicted. This is due to the angles used for the wedges on the guides and on the bottom of the disc. During design and testing, care was taken through the efforts listed above to conserve the amount of force when driving the valve disc 166 into the seat 128, but it was determined that the valve disc 166 can be driven into the seat with full pressure and only very little force is used to extract the disc from the seat. For example, when driving the valve disc 166 into its seat at 8,800 lb / sf to reach the fully closed position, it was expected that 10,000 lb / sf to 12,000 lb / sf would be required to open the valve, but testing showed that only 300 lb / sf to 350 lb / sf was required to reopen the valve disc 166. The disc 166 was fully closed multiple times to prove that the valve disc 166 would not stick in the closed position.

[0059]

[0075] Under normal operation, the valve disc 166 is normally at 50% of the port open position, and the valve disc 166 can still be closed under operating conditions. Because this condition of the valve disc 166 being closed exists, the fluid control system for the valve is programmed to "control the thrust" in the closing direction. This control is part of the functionality of the present slide valve design to ensure that it always has a higher power capability to pull the valve disc open from the closed position.

[0060]

[0076] The slide gate valve 10 is used to control the flow of gas, liquid, and catalyst material in a fluid catalytic cracking process and has a valve body 12 having an internal chamber 34 formed with an inlet 48 and an outlet 50. The valve 10 has an orifice plate 92 positioned within the chamber 34, the orifice plate 92 formed with an orifice 114. The valve 10 further has a first disc guide 136A and a second disc guide 136B positioned on either side of the orifice 114, the disc guide 136A and the disc guide 136B each having a guide channel 146 and a wedge 160 having a wedge surface 162. The valve 10 further includes a valve disc 166 positioned between a first valve body guide 136A and a second valve body guide 136B, and the valve disc 166 is configured to slide along the valve body guides 136A-B from a fully open position in which gas, liquid, and catalytic material can pass through the orifice to a fully closed position in which the orifice 114 is blocked to prevent flow of gas, liquid, or catalytic material through the orifice.

[0061]

[0077] A valve disc 166 has a pair of wedges 184A-B each having a wedge surface 186. Movement of the valve disc 166 from the fully open position toward the fully closed position causes the valve disc 166 to slide linearly along the first and second plug guides 136A-B until a point in the movement of the valve disc 166 at which the wedges 184A-B of the valve disc 166 engage the wedges 160 of the first and second plug guides 136A-B, thereby translating the valve disc 166 toward the orifice plate 92, thereby sealing the valve disc 166 against the orifice plate 92, thereby blocking flow through the orifices 114. The orifice plate 92 has a refractory material 122 positioned radially outward from the orifices 114 and a sealing surface 126 positioned radially outward from the refractory material 122.

[0062]

[0078] The sealing surface 126 has a layer of STELLITE alloy. The first and second disc guides 136A, 136B each have a first end 138 and a second end 140, with a wedge 160 located closer to the second end 140 compared to the first end 138, the wedge being integral with the first and second disc guides 136A, 136B. The first and second disc guides each have a guide channel 146 and a flat interior wall 142, where the wedge 160 extends outwardly from the interior wall 142. The valve disc 166 has a top surface having a central region having a refractory material 195 and a seat ring member 193 positioned radially outward from the central region adapted to seal against the sealing surface 126 of the orifice plate 92 when the valve disc 166 is in the fully closed position. The valve disc 166 has a nose 197 and refractory material 191 surrounding the nose 197 of the valve disc 166. Wedges 184A-B of the valve disc 166 are integral with the valve disc 166. The valve disc 166 is formed with a slot 192 configured to receive an end 200 of an actuator stem 196 which is moved along an axis 180 by the actuator 20, where the connection of the actuator stem 196 to the valve disc 166 allows the valve disc 166 to move relative to the actuator stem 196 as the valve disc 166 is moved from a fully open position to a fully closed position. The actuator 120 is configured to periodically partially retract the actuation stem 196 and the valve disc 166 along the linear axis 180 to a partially retracted, non-sealing position such that the valve disc 166 is not in sealing engagement with the orifice plate 92 and is spaced a short distance from the orifice plate 91, thereby creating a gap and moving the valve disc 166 back to the fully closed position.

[0063]

[0079] While various features of the present invention have been specifically shown and described in connection with exemplary embodiments thereof, it should be understood that these specific arrangements are merely exemplary, and that the present invention is to be accorded its broadest interpretation within the terms of the appended claims.

Claims

1. 1. A slide gate valve for controlling the flow of gas, liquid, and catalyst material in a fluid catalytic cracking process, comprising: a valve body having an interior chamber formed with an inlet and an outlet; an orifice plate positioned within the chamber and configured to have an orifice; first and second valve body guides positioned on opposite sides of the orifice, each having a guide channel and a wedge having a wedge surface; a valve disc positioned between the first and second disc guides and configured to slide along the disc guide from a fully open position, in which gas, liquid, and catalytic material may pass through the orifice, to a fully closed position, in which the orifice is blocked to prevent flow of gas, liquid, or catalytic material through the orifice, the valve disc having a pair of wedges, each wedge having a wedge surface; Equipped with movement of the valve disc from the fully open position toward the fully closed position causes the valve disc to slide linearly along the first and second plug guides to a point in the valve disc's movement; at said point, said wedges on said valve disc engage said wedges on said first and second valve body guides, translating said valve disc towards said orifice plate, sealing said valve disc against said orifice plate and blocking flow through said orifice. Slide gate valve.

2. the orifice plate includes a refractory material positioned radially outward from the orifices.

2. The slide gate valve of claim 1.

3. the orifice plate having a sealing surface positioned radially outward from the refractory material.

3. The slide gate valve according to claim 2.

4. the sealing surface having a layer of Stellite alloy; 4. The slide gate valve according to claim 3.

5. each of the first valve body guide and the second valve body guide has a first end and a second end; the wedge is closer to the second end compared to the first end; 2. The slide gate valve of claim 1.

6. the wedge is integral with the first and second valve body guides; 6. The slide gate valve according to claim 5.

7. each of the first valve body guide and the second valve body guide has a guide channel and a flat interior wall; the wedge extends outwardly from the interior wall; 6. The slide gate valve according to claim 5.

8. the valve disc having a top surface with a central region having a refractory material; 4. The slide gate valve according to claim 3.

9. the valve disc having a seat ring member positioned radially outward from the central region; the seat ring member is adapted to seal against the sealing surface of the orifice plate when the valve disc is in the fully closed position.

9. The slide gate valve of claim 8.

10. the valve disc having a nose and a fire resistant material surrounding the nose of the valve disc; 10. The slide gate valve of claim 9.

11. the wedge of the valve disc is integral with the valve disc; 2. The slide gate valve of claim 1.

12. the valve disc is formed with a slot configured to receive an end of an actuator stem; a connection of the actuator stem to the valve disc that permits movement of the valve disc relative to the actuator stem as the valve disc is moved from the fully open position to the fully closed position; 2. The slide gate valve of claim 1.

13. 1. A slide gate valve for controlling the flow of gas, liquid, and catalyst material in a fluid catalytic cracking process, comprising: a valve body having an interior chamber formed with an inlet and an outlet; an orifice plate positioned within the chamber and configured to have an orifice; first and second valve body guides positioned on opposite sides of the orifice, each having a guide channel and a wedge having a wedge surface; a valve disc positioned between the first and second disc guides and configured to slide along the disc guide from a fully open position, in which gas, liquid, and catalytic material may pass through the orifice, to a fully closed position, in which the orifice is blocked to prevent flow of gas, liquid, or catalytic material through the orifice, the valve disc having a pair of wedges, each wedge having a wedge surface; an actuator stem having a first end coupled to the valve disc; an actuator coupled to a second end of the actuator stem, the actuator and the actuator stem adapted to move the valve disc from the fully open position to the fully closed position; and Equipped with movement of the valve disc from the fully open position toward the fully closed position causes the valve disc to slide linearly along the first and second plug guides to a point in the valve disc's movement; at said point, said wedges on said valve disc engage said wedges on said first and second valve body guides, translating said valve disc towards said orifice plate, sealing said valve disc against said orifice plate and blocking flow through said orifice. Slide gate valve.

14. the actuator periodically partially retracts the actuation stem and the valve disc along a linear axis to a partially retracted, non-sealing position; the valve disc is not sealingly engaged with the orifice plate and is spaced a short distance from the orifice plate to create a gap and move the valve disc back to the fully closed position; 14. The slide gate valve of claim 13.

15. the valve disc is formed with a slot configured to receive an end of an actuator stem; a connection of the actuator stem to the valve disc that permits movement of the valve disc relative to the actuator stem as the valve disc is moved from the fully open position to the fully closed position; 14. The slide gate valve of claim 13.

16. the orifice plate includes a refractory material positioned radially outward from the orifices.

14. The slide gate valve of claim 13.

17. the orifice plate having a sealing surface positioned radially outward from the refractory material.

17. The slide gate valve of claim 16.

18. the valve disc having a top surface with a central region having a refractory material; 14. The slide gate valve of claim 13.

19. the valve disc having a seat ring member positioned radially outward from the central region; the seat ring member is adapted to seal against the sealing surface of the orifice plate when the valve disc is in the fully closed position.

20. The slide gate valve of claim 18.

20. 1. A slide gate valve for controlling the flow of gas, liquid, and catalyst material in a fluid catalytic cracking process, comprising: a valve body having an interior chamber formed with an inlet and an outlet; an orifice plate positioned within the chamber, the orifice plate being formed with an orifice; a valve body guide positioned adjacent to the orifice, the valve body guide having a guide channel; a valve disc configured to slide along the guide channel of the valve body guide from a fully open position, in which gas, liquid, and catalytic material may pass through the orifice, to a fully closed position, in which the orifice is blocked to prevent flow of gas, liquid, or catalytic material through the orifice; a cam located within the interior chamber of the valve body; Equipped with movement of the valve disc from the fully open position toward the fully closed position causes the valve disc to slide linearly along the guide channel of the valve disc guide to a point in the valve disc's movement; at said point, said cam translates said valve disc towards said orifice plate, sealing said valve disc against said orifice plate to block flow through said orifice. Slide gate valve.

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