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WO1997036664A1 - Filtre d'aspiration a capacite elevee et perte de charge limitee pour reacteurs nucleaires - Google Patents

Filtre d'aspiration a capacite elevee et perte de charge limitee pour reacteurs nucleaires Download PDF

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Publication number
WO1997036664A1
WO1997036664A1 PCT/US1997/005336 US9705336W WO9736664A1 WO 1997036664 A1 WO1997036664 A1 WO 1997036664A1 US 9705336 W US9705336 W US 9705336W WO 9736664 A1 WO9736664 A1 WO 9736664A1
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WO
WIPO (PCT)
Prior art keywords
strainer
radius
intake
disks
disk
Prior art date
Application number
PCT/US1997/005336
Other languages
English (en)
Inventor
Alan J. Bilanin
Andrew E. Kaufman
Original Assignee
Continuum Dynamics, Inc.
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from US08/780,582 external-priority patent/US5759399A/en
Application filed by Continuum Dynamics, Inc. filed Critical Continuum Dynamics, Inc.
Publication of WO1997036664A1 publication Critical patent/WO1997036664A1/fr

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Classifications

    • G—PHYSICS
    • G21—NUCLEAR PHYSICS; NUCLEAR ENGINEERING
    • G21C—NUCLEAR REACTORS
    • G21C19/00—Arrangements for treating, for handling, or for facilitating the handling of, fuel or other materials which are used within the reactor, e.g. within its pressure vessel
    • G21C19/28—Arrangements for introducing fluent material into the reactor core; Arrangements for removing fluent material from the reactor core
    • G21C19/30—Arrangements for introducing fluent material into the reactor core; Arrangements for removing fluent material from the reactor core with continuous purification of circulating fluent material, e.g. by extraction of fission products deterioration or corrosion products, impurities, e.g. by cold traps
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B01—PHYSICAL OR CHEMICAL PROCESSES OR APPARATUS IN GENERAL
    • B01D—SEPARATION
    • B01D29/00—Filters with filtering elements stationary during filtration, e.g. pressure or suction filters, not covered by groups B01D24/00 - B01D27/00; Filtering elements therefor
    • B01D29/11—Filters with filtering elements stationary during filtration, e.g. pressure or suction filters, not covered by groups B01D24/00 - B01D27/00; Filtering elements therefor with bag, cage, hose, tube, sleeve or like filtering elements
    • B01D29/111—Making filtering elements
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B01—PHYSICAL OR CHEMICAL PROCESSES OR APPARATUS IN GENERAL
    • B01D—SEPARATION
    • B01D29/00—Filters with filtering elements stationary during filtration, e.g. pressure or suction filters, not covered by groups B01D24/00 - B01D27/00; Filtering elements therefor
    • B01D29/11—Filters with filtering elements stationary during filtration, e.g. pressure or suction filters, not covered by groups B01D24/00 - B01D27/00; Filtering elements therefor with bag, cage, hose, tube, sleeve or like filtering elements
    • B01D29/31—Self-supporting filtering elements
    • B01D29/33—Self-supporting filtering elements arranged for inward flow filtration
    • B01D29/333—Self-supporting filtering elements arranged for inward flow filtration with corrugated, folded filtering elements
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B01—PHYSICAL OR CHEMICAL PROCESSES OR APPARATUS IN GENERAL
    • B01D—SEPARATION
    • B01D29/00—Filters with filtering elements stationary during filtration, e.g. pressure or suction filters, not covered by groups B01D24/00 - B01D27/00; Filtering elements therefor
    • B01D29/39—Filters with filtering elements stationary during filtration, e.g. pressure or suction filters, not covered by groups B01D24/00 - B01D27/00; Filtering elements therefor with hollow discs side by side on, or around, one or more tubes, e.g. of the leaf type
    • B01D29/43—Filters with filtering elements stationary during filtration, e.g. pressure or suction filters, not covered by groups B01D24/00 - B01D27/00; Filtering elements therefor with hollow discs side by side on, or around, one or more tubes, e.g. of the leaf type mounted otherwise than transversely on the tube mounted otherwise than axially on the tube
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B01—PHYSICAL OR CHEMICAL PROCESSES OR APPARATUS IN GENERAL
    • B01D—SEPARATION
    • B01D29/00—Filters with filtering elements stationary during filtration, e.g. pressure or suction filters, not covered by groups B01D24/00 - B01D27/00; Filtering elements therefor
    • B01D29/88—Filters with filtering elements stationary during filtration, e.g. pressure or suction filters, not covered by groups B01D24/00 - B01D27/00; Filtering elements therefor having feed or discharge devices
    • B01D29/92—Filters with filtering elements stationary during filtration, e.g. pressure or suction filters, not covered by groups B01D24/00 - B01D27/00; Filtering elements therefor having feed or discharge devices for discharging filtrate
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B01—PHYSICAL OR CHEMICAL PROCESSES OR APPARATUS IN GENERAL
    • B01D—SEPARATION
    • B01D2201/00—Details relating to filtering apparatus
    • B01D2201/02—Filtering elements having a conical form
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B01—PHYSICAL OR CHEMICAL PROCESSES OR APPARATUS IN GENERAL
    • B01D—SEPARATION
    • B01D2201/00—Details relating to filtering apparatus
    • B01D2201/44—Special measures allowing the even or uniform distribution of fluid along the length of a conduit
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E30/00—Energy generation of nuclear origin
    • Y02E30/30—Nuclear fission reactors

Definitions

  • TITLE HIGH CAPACITY, LOW HEAD LOSS, SUCTION STRAINER
  • the invention relates to a suction strainer for use on suction lines in nuclear reactors m which the internal radius of the central core decreases with increased distance from the intake of the strainer.
  • Truncated cone strainer 10 includes a perforated surface 12, a center line 14 around x axis 18, and an internal radius r(x) 16 between center line 14 and perforated surface 12.
  • the truncated cone strainer 10 of Fig. 1A is a relatively inexpensive and simple structure.
  • the stacked disk strainer 20 illustrated in Fig. 1B improves upon the truncated cone strainer of Fig. 1A by providing more surface area to accumulate debris within the same overall strainer volume envelope.
  • the stacked disk strainer 20 mcludes a perforated surface 22, a center line 24 about x axis 28 and an internal radius r(x) 26 between center line 24 and the innermost surface 26. It is clear that the stacked disk strainer area of the prior an embodiment 20 of Fig 1B can be made arbitrarily large by decreasing both the distance between the disks and the disk thickness, thereby adding more disks within a given volume. Accordingly, a measure of strainer performance can be obtained by dividing the strainer surface area by the strainer volume, especially when strainer volumes are comparable.
  • strainer 30 includes a perforated, cylindrical outer surface 32, a conical bottom 34, a center line 38 about the x axis and an internal radius r(x) 36 between surface 32 and center line 38.
  • Strainer flange 40 connects to pump suction intake flange 42. Note that the approach velocities U a 44 are highest closest to flanges 40, 42.
  • strainer 50 illustrated in Fig. 2B, includes inserts which internally modify the nature of the strainer.
  • Strainer 50 includes a perforated surface 52, a conical bottom 54, a center line 58 around the x axis and an internal radius r(x) 56 between the center line 58 and surface 52.
  • Strainer flange 60 attaches to pump suction intake flange 62.
  • a cylindrical insert 66 is located inside of strainer 50. Inserts 66 improve the uniformity of the approach velocity U a 64, but may introduce other drawbacks.
  • Fig. 2 of U.S. Patent 5,539,790 shows a prior art strainer similar to that illustrated as prior art in Fig. 2A of this disclosure.
  • U.S. Patent 4,738,778 describes a zig-zag filter element which is suitable for certain types of applications but not for nuclear reactor suction lines.
  • the invention comprises a multiple disk strainer for use in nuclear reactor emergency suppression pools in which the inner disk radius decreases with distance from the suction intake.
  • the strainer is attached to a suction pump intake pipe and is optimally configured to have minimum head loss and accumulate a maximum amount of debris, within a given volume. Because the internal radius decreases with distance from the intake, a constant fluid flow velocity is maintained throughout the entire central core region. The constant core velocity minimizes head loss, and therefore pressure drop, where velocities are greatest and, hence, the internal fluid flow is most sensitive to irreversible head loss.
  • Surrounding the central core are a plurality of perforated disks varying in internal diameter whose thickness may be constant or may vary with distance from the intake.
  • the perforations, or holes, in each disk are sized to prevent debris from passing into the strainer, but large enough to allow fluid to pass through.
  • the spacing between the disks is generally uniform but may vary depending upon the characteristics of the debris to be strained.
  • the outer diameter of the disks is typically constant, but can vary and still maintain a constant core velocity.
  • the preferred embodiment of the strainer invention comprises a plurality of stacked disks in which the spacing between the disks is uniform and in which the disk thickness increases with distance from the intake while the internal radius of the disk decreases with distance from the intake.
  • the internal disk radius may decrease linearly or exponentially, or a combination of both, as it gets further from the suction intake.
  • the exterior diameters of the disks are preferably uniformly the same, but according to another alternative embodiment, the external diameter of the disks may decrease with increasing distance from the intake. This structure would be most advantageous where it is desired to minimize the load on the suction flange.
  • Another group of alternative embodiments comprehends the use of tapered disks rather than disks of generally uniform thickness.
  • Fig. 1A illustrates a prior art truncated cone strainer.
  • Fig. 1B illustrates a prior art, stacked disk strainer, as currently manufactured, including an inner core having a uniform, constant, internal radius.
  • Fig. 2A illustrates a prior art cylindrical strainer and the manner in which the approach velocity U a varies along the length of the strainer.
  • Fig. 2B illustrates another prior art cylindrical strainer, including an insert, which causes the approach velocity U a to be more uniform along the length of the strainer.
  • Fig. 3A is a perspective, partial, cross-sectional view of a strainer according to the preferred embodiment of the invention in which the internal radius r(x) decreases with distance from the suction intake and also wherein the thickness of the disks increases with distance from the suction intake while the disk separation remains the same throughout the length of the strainer.
  • Fig. 3B illustrates a low aspect ratio embodiment of the preferred strainer illustrated in Fig. 3A.
  • Fig. 3C illustrates a high aspect ratio embodiment of the preferred strainer illustrated in
  • Fig. 4A is an elevated, partial cross-sectional view of the preferred embodiment of the invention shown in Fig. 3A illustrating the parameters employed to describe the invention. Because the preferred embodiment illustrated in Fig. 3A is axis symmetric, only one-half of the cross-section is illustrated.
  • Fig. 4B illustrates the fluid velocities U, U a , U c and U d associated with the cross-sectional view shown in Fig. 4A.
  • Fig. 5 is an elevated, partial cross-sectional view of an embodiment in which the internal disk radius r(x) decreases exponentially with increased distance from the suction intake.
  • Fig. 6 is an elevated, partial cross-sectional view of an embodiment in which the internal disk radius r(x) decreases linearly with increased distance from the suction intake.
  • Fig. 7 is a graph of normalized internal radii r(x) as a function of the normalized distance x for the preferred embodiment illustrated in Fig. 3A showing curves for several different choices of base and outer radii.
  • Fig. 8 is a graph of normalized internal radii r(x) as a function of the normalized distance x for an exponentially varying internal radius r(x) such as seen in Fig. 5, and wherein several curves are shown based upon different base and outer radii.
  • Fig. 9 is a graph of normalized internal radii r(x) as a function of the normalized distance x from the suction intake for a linearly varying internal radius r(x) embodiment such as illustrated in Fig. 6, and wherein different curves illustrate different choices of base and outer radii.
  • Fig. 10A is a scale drawing of the preferred embodiment illustrated in Fig. 3A for a particular application.
  • Fig. 10B is a table giving the dimensions for the particular embodiment illustrated in Fig. 10A.
  • Fig. 11 is a scale cross-sectional illustration of an embodiment where the internal radius r(x) varies exponentially as shown, for example, in the embodiment of Fig. 5 and as sized for a particular application.
  • Fig. 12 is a scale cross-sectional illustration of an embodiment where the internal radius r(x) varies linearly such as shown in the embodiment of Fig. 6, and wherein the strainer is sized for a specific application.
  • Fig. 13 is a partial, cross-sectional illustration of an alternative embodiment of the invention in which the outer radius of the disks decrease with distance from the suction intake in order to minimize the hydro-dynamic moment on the suction flange.
  • Fig. 14 illustrates an alternative embodiment of the invention in which the multiple stacked disks are tapered instead of being of uniform thickness.
  • Fig. 15A illustrates the nomenclature used to describe parameters with respect to the tapered disk embodiment of Fig. 14.
  • Fig. 15B illustrates the fluid velocities U, U a , U c , and U d associated with the tapered disk strainer illustrated in Figs. 14 and 15A.
  • Fig. 16 is an elevated, partial cross-sectional view of the tapered disk embodiment in which the internal radius r(x) decreases exponentially with distance from the suction intake.
  • Fig. 17 is an elevated, partial cross-sectional view of the tapered disk embodiment in which the internal disk radius r(x) decreases linearly with distance from the suction intake.
  • Fig. 18 is a partial cross-sectional view of the tapered disk embodiment in which the internal disk angle ⁇ is constant.
  • Fig. 19 is a graph illustrating normalized internal radii r(x) as a function of the normalized distance x for the tapered disk embodiment with t(x) ⁇ l and also showing other curves for different base and outer radii.
  • Fig. 20 is a graph illustrating normalized internal radii r(x) as a function of the normalized distance x for an exponentially varying internal radii for the tapered disk embodiment in which the disks have a constant thickness and wherein several curves are shown based upon different base and outer radii.
  • Fig. 21 is a graph of a normalized internal radii r(x) as a function of the normalized distance x from the suction intake as it decreases linearly with increased distance from the suction intake but keeping the disk thickness relatively constant and also showing other curves for different base and outer radii.
  • Fig. 22 is a graph of a normalized internal radii r(x) as a function of the normalized distance x from the suction intake for a constant disk angle ⁇ and constant U d .
  • Fig. 23 is a graph of normalized internal radii r(x) as a function of the normalized distance x from the suction intake for a constant disk angle ⁇ and a constant U.
  • Fig. 24A is a scale drawing of the tapered disk embodiment such as illustrated in Fig. 14 as sized for a particular application.
  • Fig. 24B is a table of dimensions for the particular embodiment illustrated in Fig. 24A.
  • Fig. 25 is a scale drawing of the tapered embodiment, such as illustrated in Fig. 14, with the transition to a linear variation of internal radius r(x) occurring closer to the suction flange or intake.
  • Fig. 26 illustrates a tapered disk embodiment in which the internal radius r(x) decreases linearly with distance from the suction intake and wherein the disk thickness remains substantially constant.
  • Fig. 27 illustrates the tapered disk embodiment in which the internal radius r(x) decreases exponentially with distance from the suction intake and wherein the disk thickness remains substantially constant.
  • Fig. 28 illustrates the tapered disk embodiment in which the disk angle ⁇ and U d remain substantially constant.
  • Fig. 29 illustrates the parameters and nomenclature used to calculate the pressure drop and debris bed buildup.
  • Fig. 30 illustrates an embodiment of the invention in which support plates are placed between the stacked disks and wherein the plates are preferably equally spaced.
  • the preferred embodiment 100 of the suction strainer is illustrated in Fig. 3A.
  • Prefened embodiment 100 comprises a plurality of stacked, perforated disks 102a - 102f with varying internal radii r(x) and thickness t(x) as shown in Fig. 4A.
  • Each strainer 100 includes a plurality of stacked disks 102a - 102f.
  • Each disk 102a - 102f has an associated first forward facing face 112a - 112f, a second rearward facing face 116a - 116f and an outwardly facing circumferential surface 114a - 114f.
  • Each disk 102a - 102f includes an inwardly facing surface 118a - 118e that separates it from its neighboring disk.
  • Inwardly facing surfaces 118a - 118e define a tapered core having a radius r(x) 106 around a central axis 104.
  • the preferred embodiment 100 has a central core 105 which is symmetrical about center line 104, also refened to as the x axis, because the prefened embodiment 100 is best defined in cylindrical units.
  • Central core 105 is attached by a flange 110 to a conventional suction pump intake at one end and is terminated at the distal end by plate 108.
  • the internal radius r(x) decreases with distance from the suction intake, i.e., strainer flange 110, whereas the thickness of t(x) of each disk 102a - 102f increases with distance from the suction intake thereby maximizing the amount of debris that can be accumulated while minimizing strainer head loss within a given overall size or volume envelope.
  • the preferred embodiment 100 of the invention can be built with a low aspect ratio as shown by embodiment 120 of Fig. 3B or a high aspect ratio as indicated by embodiment 140 illustrated in Fig. 3C.
  • Low aspect ratio embodiment 120 includes three disks 122a - 122c.
  • the low aspect ratio embodiment 120 also includes a varying internal radius r(x) 126 as measured about center line 124.
  • the internal central core 125 is widest near the suction intake flange 130 and terminates at a distal plate 128.
  • the low aspect ratio embodiment 120 includes fewer strainer disks 122a - 122c, but an individual disk may have a relatively large external diameter.
  • the high aspect ratio embodiment 140 includes a larger number of strainer disks 142a - 142f, but each individual disk might have a smaller external diameter than the strainer disks 122a - 122c of the low aspect embodiment 120 illustrated in Fig. 3B.
  • the low aspect embodiment 120 is, therefore, relatively low and squat as compared to the high aspect ratio embodiment 140 which is relatively long and thin. It therefore follows that the central core
  • 145 of the high aspect embodiment 140 has an internal radius r(x) 146 that varies more gradually about x axis 144 from the intake suction flange 150 towards the distal end plate 148.
  • the preferred embodiment 100 of the invention is preferably formed from perforated stainless steel plate with 1/8" round holes on 3/16th" staggered centers.
  • the perforated plate material is employed on the forward facing surfaces 112a-112f, on the rearward facing surfaces 116a - 116f and on the outward circumferential surfaces 114a - 114f.
  • Figs. 4A and 4B The nomenclature and parameters used to describe the geometry of the suction strainers and the related flow fields are illustrated in Figs. 4A and 4B.
  • the parameters illustrated in Fig. 4A are identified as follows:
  • strainers fabricated according to the preferred embodiment 100 of the invention are to minimize head loss and to collect debris where velocities U are low, since the pressure drop across the debris bed is known to scale with the velocity or the velocity squared through the bed.
  • the velocities have the following characteristics:
  • the highest velocities are found in the central region 105 of the core and are identified as velocity U c .
  • Velocities across the strainer surfaces 112a - 112e, 114a - 114e, 116a - 116d and 118a - 118d which determine the debris growth rate are designated as U.
  • the velocity of the fluid leaving the stacked disks 102a - 102e and entering the central core 105 of the strainer is denoted by U d .
  • a major purpose of the present invention is to minimize the acceleration of the fluid internal to the strainer 100 in regions where velocities are large. Accordingly, the families of internal geometries described by the function r(x) are limited to keep the velocities U c constant or nearly constant. A consequence of this novel approach is that the pressure drop along the central axis 104 is zero or nearly zero. Also, by controlling the thickness t(x) of the disks 102a
  • the ratio of U d /U c can be independently controlled for each disk.
  • the radius of the central core region r(x) 106 varies linearly, or exponentially, or both, in the x direction 104 such that the radius r(x) 106 is a minimum at its greatest distance from the suction source and suction flange 110.
  • This relationship helps to maintain a constant core velocity U c in the x direction 104, a specified velocity entering the core 105 from each disk U d , and a constant velocity entering each disk U.
  • a consequence of this novel structure is that while the velocity in the core region U c remains constant, the volumetric, or mass, flow rate increases as x increases toward the suction flange 110.
  • the preferred embodiment 100 is illustrated in Fig. 3A, but it will be understood that the invention is not necessarily limited to the external shape or proportions illustrations in Fig. 3A. It could have, for example, a higher or lower aspect ratio as illustrated in Figs. 3B and 3C.
  • each disk 102a - 102f varies correspondingly with the internal radius r(x) 106 such that the ratio of the disk surface area to the internal transverse disk area (i.e., 2 ⁇ r(x) t(x)) at the interface to the core region 105 remains constant and equal for all disks.
  • the head loss associated with the fluid leaving each disk 102a - 102f, respectively, and entering the core flow is essentially independent of the location of each individual strainer disk.
  • the fluid entering the core 105 for each disk 102a - 102f turns through approximately the same angle. Keeping the same turning geometry for each disk 102a - 102f minimizes the mixing and turning losses associated with the strainer 100 as a whole. This characteristic, combined with the constant core velocity U c , minimizes the strainer head loss without debris and helps establish the desired distribution of debris loading in order to minimize head loss at all debris loadings.
  • the velocity U through the disk surfaces is nearly constant.
  • the strainer 100 develops a nonuniform approach velocity U a because the area of the disks 102a - 102f changes as a function of x.
  • the approach velocity U a is shown in Fig. 4B.
  • This nonuniform approach velocity U a allows the invention to optimally distribute fiber in order to develop minimum head loss.
  • the invention utilizes the volume between disks 102a - 102f to accumulate debris at the same rate without developing excessive head loss. For example, if the spacing between disks 102a and 102b is 20% full, then the spacing between the other disks is likewise 20% full.
  • FIG. 5 An alternative embodiment of the invention 160 is illustrated in Fig. 5.
  • embodiment 1 An alternative embodiment of the invention 160 is illustrated in Fig. 5.
  • the velocity U d varies with x while still maintaining a constant core velocity U c around center line 164.
  • the radius r(x) 166 between center line 164 and inner surfaces 170a - 170d varies exponentially with x.
  • the internal radius r(x) 166 decreases the further the radius r(x) is from the pump intake suction flange and the closer it comes to the end plate 168.
  • FIG. 6 Another alternative embodiment 180 is illustrated in Fig. 6.
  • the internal radius r(x) 186 between center line 184 and internal surfaces 190a - 190d of disks 182a - 182e varies linearly as distance increases from the pump suction intake flange and as it approaches the end plate 188.
  • the thickness of each of the disks 182a is illustrated in Fig. 6.
  • Embodiment 180 approaches, but does not achieve, minimum internal head loss because of the approximation made to the internal radial profile.
  • Embodiment 180 may be simpler to manufacture and still preserve the desired nonuniform approach velocity U a .
  • the external radius need not be constant and the invention 180 is not limited to the external shape or proportions illustrated in Fig. 6.
  • the relationship between the inner radius of the disks r(x) and the distance along the strainer axis 104 is determined as
  • N L/(l + t)
  • the disk thickness, t(x), is constant and the number of disks, N, is determined according to the following relationship:
  • N L/(l + t)
  • Fig. 7 is a graph which illustrates the principles described for a family of inner disk radii r(x) for the preferred embodiment 100 illustrated in Fig. 3A. If the disk thickness t(x) is held constant such that the velocity, U d , leaving the disks is not constant, the result is a family of inner disk radii r(x) illustrated in the table of Fig. 8. If the velocity through the strainer surface is permitted to vary with distance along the strainer, this results in a linear variation of the strainer inner radius r(x) as illustrated in the table of Fig. 9.
  • Figures 7-9 illustrate a portion of the range of shapes the invention can take for different design inputs.
  • the strainer had a surface area of 273 square feet and included 18 disks with a profile such as shown in Fig. 10A.
  • the fabrication dimensions are given in the table of Fig. 10B.
  • the design cross section changes to that illustrated in Fig. 12.
  • the strainer surface varies with x and the strainer area was determined to be 207 square feet.
  • the strainer area nearest the suction flange 210 it may be desirable to locate the strainer area nearest the suction flange 210 as illustrated in embodiment 200 of Fig. 13. According to this embodiment, the strainer inner radius r(x) between the inner surfaces 212a - 212d of the disks
  • the velocities U c , U d , and U are substantially constant as the internal radius r(x) between center line 204 and the inner surfaces 212a - 212d vary and decrease with distance from suction flange 210 as the radius r(x) approaches end plate 208. Note that the disk thicknesses t(x) are not constant and that the outer radius of the embodiment 200 decreases with distance from the suction flange 210.
  • Tapered disk embodiment 300 includes a plurality of tapered disks 302a - 302f around a center line 304.
  • the strainer 300 includes a strainer suction flange 310 opposite from a distal end plate 308.
  • Each of the tapered disks 302a - 302f includes a forward facing first surface 312a - 312f and a rearward facing second surface 316a - 316e connected together at an edge 314a - 314f, respectively.
  • the nomenclature to describe the geometry and fluid flow of strainer 300 are illustrated in Figs. 15A and 15B.
  • the internal radius r(x) 306 and plate thickness may vary in a prescribed way in order to maximize the amount of debris that can be accumulated while minimizing strainer head loss within a given overall size or volume envelope.
  • An important feature of the tapered strainers, which are intended to minimize head loss, is to collect debris where velocities are low, since the pressure drop across the debris bed is known to scale with a velocity or velocity squared through the bed. Hence, the strainer velocities are such that U c >U d >U. The highest velocities are in the central region of the strainer and are denoted by U c . The velocities across the strainer surface and, hence, through the debris bed, which will accumulate on those surfaces, is designated as U.
  • the velocity of the fluid leaving the stacked disks and entering the central region 305 of the strainer 300 is denoted by U d .
  • a major purpose of the tapered embodiment 300 is to minimize the acceleration of the fluid internal to the strainer 300 in regions where velocities are large. Therefore, the velocities of the internal geometries described by the function r(x) are selected to keep the velocities U c constant or nearly constant. A consequence of this feature is that the pressure drop across the axis 304 of the strainer 300 is zero or nearly zero.
  • the thickness t(x) of the disks it is possible to control the velocity of the fluid leaving the disk U d such that the mixing and acceleration loss as the fluid moves into the central core 305 of the strainer 300 is nominal.
  • the radius r(x) of the core region 305 varies linearly, exponentially, or linearly and exponentially, with x such that the radius r(x) decreases the further it is removed from the suction flange 310.
  • This helps assure that there is a constant core velocity U c in the x direction, a constant velocity entering the core 305 from each disk U d , and a constant velocity entering each disk U.
  • a consequence of this unique structure 300 is that while the velocity in the core region 305 remains constant, the volumetric (or mass) flow rate increases as x increases towards the suction flange 310 and away from the distal end plate 308.
  • the preferred embodiment 300 of the tapered plate version of the invention is shown in Fig. 14 but is not necessarily limited to the external shape or proportions illustrated.
  • the disks 302a - 302f are shown tapered to a point 314a - 314f, respectively, but for structural and flow reasons, a small minimum of thickness may also be employed.
  • each disk 302a - 302f varies correspondingly with the internal radius r(x) 306 such that the ratio of the disk surface area to the internal transverse disk area (2 ⁇ r(x) t(x)) at the interface to the core region 305 remains constant and equal for all disks.
  • the head loss associated with the fluid leaving each disk 302a - 302f and entering the core flow U c is essentially independent of its location in the strainer 300.
  • the fluid entering the core from each disk 302a - 302f turns through approximately the same angle. Maintaining geometrically similar turning angles minimizes the mixing and turning losses in the strainer 300.
  • This feature combined with the constant velocity core, minimizes the strainer head loss without debris and helps establish the desired distribution of debris loading to provide minimum head loss at all debris loadings.
  • the velocity through the disk surfaces 312a - 312f and 316a - 316e is nearly constant.
  • the strainer 300 develops a nonuniform approach velocity because the area of the disks 302a - 302f changes as a function of x.
  • the approach velocity U a is illustrated in Fig. 15B. This nonuniform approach velocity allows the invention 300 to optimally distribute fiber to develop minimum head loss.
  • the invention 300 utilizes the volume between the disks to accumulate debris without developing excessive head loss.
  • the internal radius r(x) variation depends upon the thickness t(x) of the disks compared to the spacing d(x) between the disks 302a - 302f.
  • the disk thickness t(x) is less than the nominal spacing d(x)
  • the square of the radius r(x) varies exponentially in the x direction.
  • the radius r(x) varies linearly with x.
  • the thicker disks are found away from the suction flange 310 of the strainer 300.
  • An alternative embodiment 320 of the invention allows the disk thickness t(x) to be constant at the inner radius r(x) and independent of x.
  • the velocity U varies with x while still maintaining a constant core velocity U c and a constant velocity exiting the disks into the core U d .
  • the radius r(x) varies exponentially with x.
  • a cross sectional view of this embodiment is illustrated in Fig. 16. Similar to the varying disk thickness embodiment 300, the outer radius of embodiment 320 need not be constant and is not limited to the external shape or proportions illustrated in Fig. 16. Embodiment 320 may be appropriate for applications where the internal head loss is not as critical.
  • Embodiments 300 and 320 have an internal radius r(x) that varies similarly to the proportions of the preferred embodiment corresponding to the region where the thickness is greater than the nominal spacing and the region where the thickness is less than the nominal spacing, respectively, so that there is a constant velocity U d exiting the disks into the core U c .
  • FIG. 17 Another embodiment 340 of the tapered disk invention is illustrated in Fig. 17.
  • the inner radius r(x) varies linearly with x.
  • the outer radius need not be constant and the invention is not limited to the external shape or proportions illustrated in Fig. 17.
  • Another tapered disk embodiment 350 is illustrated in Fig. 18.
  • the radius r(x) varies linearly and exponentially with x.
  • This embodiment approaches, but does not achieve, the theoretical minimum internal head loss because of the approximation made to the internal radial profile.
  • embodiment 350 may be simpler to manufacture and still preserve the desired nonuniform approach velocity.
  • the outer radius of embodiment 350 need not be constant and the invention is not limited to the external shape or proportions illustrated in Fig. 18.
  • the preferred tapered disk embodiment 300 has the following parameters:
  • the relationship between the inner radius r(x) of the disks and the distance along the axis of the strainer X can be computed from the following:
  • the number of disks, N, in this embodiment is given by
  • the family of curves shown in Figs. 19 and 21 can be combined for some embodiments where the internal radial variation changes from exponential to linear.
  • Figs. 22 and 23 illustrate the internal radial variation with x for the case of constant angle ⁇ disks, with U d and U held constant, respectively.
  • Figures 19-23 illustrate a portion of the range of shapes the invention can take for different design inputs.
  • a tapered disk embodiment 300 was constructed from the design principles set forth above with the following geometrical constraints:
  • the strainer of this example had a surface area of 336 sq. feet and 24 disks.
  • the cross section of this example is illustrated in Fig. 24A and was constructed with the fabrication dimensions given in the table of Fig. 24B.
  • Fig. 25 is a scale drawing of the tapered disk embodiment with a greater minimum thickness. This produces a larger portion of the strainer where r(x) varies linearly.
  • Fig. 26 illustrates a scale drawing of a linearly varying r(x)
  • Fig. 27 illustrates a scale drawing of an exponentially varying r(x).
  • a scale illustration of a constant disk angle ⁇ embodiment is illustrated in Fig. 28.
  • Fig. 29 is a schematic view of a typical tapered disk and the relevant nomenclature.
  • the head loss, ⁇ h 1 , across the debris bed is linearly proportional to the thickness of the debris, T 1 , and the velocity through the bed, U 1 , and can be written as:
  • tapered disk embodiment 360 includes a plurality of tapered disks 362a - 362f. Each tapered disk 362a - 362f includes a forward facing surface 372a - 372f and a rearward facing surface 376a - 376e.
  • Embodiment 360 includes a central x axis 364 and an internal radius r(x) 366 which decreases with distance from the suction flange 370.
  • An end plate 368 defines the distal extreme from the suction flange 370.
  • External supports 378a - 378e are preferably plates parallel to the center line 364. The supports could comprise other structural elements such as rods, etc. The space between the external supports
  • the number and spacing of the external supports 378a - 378e depends upon the debris packing characteristics and the inherent structural strength of the strainer 360.

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  • Chemical & Material Sciences (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • Physics & Mathematics (AREA)
  • Engineering & Computer Science (AREA)
  • Plasma & Fusion (AREA)
  • General Engineering & Computer Science (AREA)
  • High Energy & Nuclear Physics (AREA)
  • Filtration Of Liquid (AREA)

Abstract

Filtre d'aspiration (100) servant à filtrer l'eau provenant de la cuve d'élimination d'urgence d'un réacteur nucléaire à eau bouillante. Ce filtre d'aspiration comprend une pluralité de disques perforés empilés (102a-102f) possédant un noyau central (105) dont le rayon intérieur minimum r(x) (106) diminue en fonction de l'augmentation de la distance depuis l'orifice d'aspiration (110) du filtre, de telle sorte que le noyau (105) présente un profil conique. Le rayon intérieur r(x) peut varier de façon linéaire (186) ou exponentielle (166) ou selon une combinaison des deux. Les disques perforés empilés (102a-102f) comprennent chacun une première surface (112a-112f) tournée vers l'orifice d'aspiration et une deuxième surface (116a-116e) tournée dans le sens contraire. Une bande périphérique (114a-114f) peut relier la première et la deuxième surfaces.
PCT/US1997/005336 1996-04-01 1997-03-28 Filtre d'aspiration a capacite elevee et perte de charge limitee pour reacteurs nucleaires WO1997036664A1 (fr)

Applications Claiming Priority (6)

Application Number Priority Date Filing Date Title
US1470396P 1996-04-01 1996-04-01
US60/014,703 1996-04-01
US1724096P 1996-05-10 1996-05-10
US60/017,240 1996-05-10
US08/780,582 US5759399A (en) 1997-01-08 1997-01-08 High capacity, low head loss, suction strainer for nuclear reactors
US08/780,582 1997-01-08

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WO1997036664A1 true WO1997036664A1 (fr) 1997-10-09

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Cited By (4)

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WO2001039208A1 (fr) * 1999-11-24 2001-05-31 Performance Contracting, Inc. Systeme de crepine dotee d'un tube central interne
US6491818B2 (en) 1995-08-24 2002-12-10 Performance Contracting, Inc. Suction strainer with an internal core tube
US9672947B2 (en) 2004-11-15 2017-06-06 Atomic Energy Of Canada Limited Finned strainer
EP2632564B1 (fr) * 2010-10-29 2018-12-26 Corning Incorporated Appareil de filtration à plaques en céramique poreuse

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ATE316413T1 (de) 2004-01-29 2006-02-15 Cci Ag Schutzsieb zum abschirmen eines saugraums
US7848475B2 (en) * 2004-05-14 2010-12-07 Continuum Dynamics, Inc. Low head loss modular suction strainer with contoured surfaces
JP4875673B2 (ja) * 2008-07-31 2012-02-15 三菱重工業株式会社 原子炉格納容器用ストレーナ
JP6580951B2 (ja) * 2015-11-09 2019-09-25 株式会社東芝 原子炉注水システム及びストレーナ洗浄用装置

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Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6491818B2 (en) 1995-08-24 2002-12-10 Performance Contracting, Inc. Suction strainer with an internal core tube
WO2001039208A1 (fr) * 1999-11-24 2001-05-31 Performance Contracting, Inc. Systeme de crepine dotee d'un tube central interne
US9672947B2 (en) 2004-11-15 2017-06-06 Atomic Energy Of Canada Limited Finned strainer
US11361870B2 (en) 2004-11-15 2022-06-14 Atomic Energy Of Canada Limited Finned strainer
EP2632564B1 (fr) * 2010-10-29 2018-12-26 Corning Incorporated Appareil de filtration à plaques en céramique poreuse

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JP3002431B2 (ja) 2000-01-24
JPH1048382A (ja) 1998-02-20

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