WO1992013710A1 - Dispositif a vis et elements de compression reglables - Google Patents

Dispositif a vis et elements de compression reglables Download PDF

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Publication number
WO1992013710A1
WO1992013710A1 PCT/US1992/000939 US9200939W WO9213710A1 WO 1992013710 A1 WO1992013710 A1 WO 1992013710A1 US 9200939 W US9200939 W US 9200939W WO 9213710 A1 WO9213710 A1 WO 9213710A1
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WO
WIPO (PCT)
Prior art keywords
housing
screw
bore
discharge
casing
Prior art date
Application number
PCT/US1992/000939
Other languages
English (en)
Inventor
James D. Foresman
H. Dale Bottorf
Original Assignee
Andritz Sprout-Bauer, 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
Application filed by Andritz Sprout-Bauer, Inc. filed Critical Andritz Sprout-Bauer, Inc.
Publication of WO1992013710A1 publication Critical patent/WO1992013710A1/fr

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B9/00—Presses specially adapted for particular purposes
    • B30B9/02—Presses specially adapted for particular purposes for squeezing-out liquid from liquid-containing material, e.g. juice from fruits, oil from oil-containing material
    • B30B9/26—Permeable casings or strainers
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B9/00—Presses specially adapted for particular purposes
    • B30B9/02—Presses specially adapted for particular purposes for squeezing-out liquid from liquid-containing material, e.g. juice from fruits, oil from oil-containing material
    • B30B9/12—Presses specially adapted for particular purposes for squeezing-out liquid from liquid-containing material, e.g. juice from fruits, oil from oil-containing material using pressing worms or screws co-operating with a permeable casing
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B9/00—Presses specially adapted for particular purposes
    • B30B9/02—Presses specially adapted for particular purposes for squeezing-out liquid from liquid-containing material, e.g. juice from fruits, oil from oil-containing material
    • B30B9/12—Presses specially adapted for particular purposes for squeezing-out liquid from liquid-containing material, e.g. juice from fruits, oil from oil-containing material using pressing worms or screws co-operating with a permeable casing
    • B30B9/121—Screw constructions

Definitions

  • the present invention relates to compression screw devices, especially of the type used for processing fiber, chip, and similar cellulosic stock material.
  • Such functions include dewatering, consolidation for feeding into a downstream piece of eguipment, and/or refining under high pressure steam or infusion of chemicals.
  • the properties of the stock material such as water content, density, effective friction, resilience, and the like, must be taken into account in designing the important variables for the compression screw device, such as required thrust, compression ratio, drainage hole size, and the like.
  • screw devices are in essence, custom designed and fabricated for each application from one of several distinct base models.
  • the devices are sized for the most severe application that can be encountered for a given base model and thus carry an unnecessary cost premium when purchased for use in a less severe application.
  • each base model is conventionally optimized with the limited objective of accomplishing the particular end use application.
  • a compression housing having a segmented outer portion adapted to support replaceable liners of varying thickness.
  • the effective flow cross section through such compression housing is thereby defined by and dependent on the variation, of only the liners, or by a combination of the liners and the unlined segments.
  • such compression housing can include drain holes, provided either in the liners, or in the outer segments.
  • anti-rotation bars can be supported to project into the screw bore an adjustable distance, without removal of the screw.
  • both the anti-rotation bars and the effective flow cross section, i.e., compression can be adjusted independently of each other.
  • the objects can also be achieved in accordance with another embodiment of the invention, in screw device configurations that may or may not have an adjustable compression housing of the type summarized immediately above.
  • an adjustable compression housing of the type summarized immediately above.
  • the combination of a novel drainage housing and an adjustable discharge housing immediately downstream of the drainage housing permits adjustment of the compression in the drainage housing.
  • the compression can be adjusted on-line, without disassembly or removal of any portion of the screw device.
  • the novel drainage housing has a plurality of coaxially stacked rings with spacers therebetween and bolts or the like traversing the rings to draw them tightly together.
  • the stacked rings thus have sufficient space to define radial channels by which pressate is drained from the screw bore defined by the internal inner diameter of the rings.
  • the inner profile of each ring has slots formed therein for supporting one or more axially extending anti-rotation bars. Notches are provided on the outer diameters of the rings for engaging frame supports to prevent rotation of the stacked assembly.
  • the spacer thickness can easily be adjusted in the shop to retain the desired drain characteristics.
  • the novel drainage housing and each of a variety of novel discharge housings, can be used independently of each other, with or without the novel compression housing aspect of the present invention.
  • the discharge housing in accordance with the present invention includes a substantially tubular casing and a cup-like bearing member supported coaxially within the casing, by plates connected between the casing and the bearing member. These plates not only support the bearing member, but also break up the condensed material as it advances from the downstream end of the screw toward the discharge opening of the device.
  • the provision of the bearing member permits the use of a screw having a stem at its downstream extremity, for rotational support within the bearing member, thereby improving performance relative to unsupported screws.
  • the discharge housing in accordance with the invention has breaker plates extending radially inwardly from the casing inner diameter at least half the radial distance to the axis.
  • the compression of the device can be adjusted by substituting a different discharge housing having a greater or lesser number of such breaker plates, or plates of thicker dimension, the preferred adjustment of compression is accomplished by providing a plurality of pegs or bolts that penetrate through the casing to project a variable distance into the discharge housing bore. These pegs not only adjust compression, but provide an additional shearing effect on the material, which can be beneficial, particularly for chemical impregnation applications.
  • the compression characteristics of virtually any type of compression screw device can be adjusted on line, by the use of a discharge end housing having the radially adjustable pegs.
  • the pegs can be manually or automatically adjusted by a process control system on line.
  • the advantages of using the adjustable pegs for compression adjustment include reduction of inventory of screw parts and screw housings, since a given screw and housing combination can be adjusted to meet a variety of compression requirements.
  • the compression can be varied without disassembling the screw press. This eliminates expensive downtime.
  • the resistance pegs contribute to the shearing and abrading action on chips, which opens up the chips for optimal chemical impregnation. The opening of the chips in the discharge housing occurs immediately before the chip plug discharges from the device and expands into the liquor bath, optimizing chemical pickup.
  • the present invention minimizes the total number of different parts and reduces engineering time for design and upkeep of drawings. This also reduces manufacturing cost and inventory costs. The number of spare parts required to be kept by the supplier and the end user is significantly reduced. Furthermore, the modular feature of the invention allows tailoring the machine to the specific application for improved performance. Such tailoring avoids the use of larger or heavier components than are required for the needs of the end user, therefore making the machines more cost effective.
  • the modularity also allows easy modification of machines operating in the field if the operating conditions change, e.g., if the machine is used for an altered feed stock. At least one of the modular components is inherently adjustable during fabrication or in the field, to optimize one or both of the compression ratio and drain hole pattern.
  • Fig. 1 is a longitudinal view of a modular compression screw device including the invention, partially cut away to reveal the screw;
  • Fig. 2 is an external perspective view looking from the discharge toward the inlet end of a modular screw device of the type shown in Figure 1;
  • Fig. 3 is a cross section view of a compression module housing but without drain holes, as would be seen if taken through lines 3-3 of Fig. 2;
  • Fig. 4 is a perspective view of another compression module housing which has drain holes
  • Fig. 5 is an elevation view of a third compression housing module, which has drain holes;
  • Fig. 6 is a cross section view taken along line 6-6 of Fig. 5;
  • Fig. 7 is an exploded perspective view of the drainage module housing of the device shown in Figure 2;
  • Figs. 8 and 9 are front and side views, respectively, of one of the plurality of rings in the drainage module housing of Figure 7;
  • Figs. 10 and 11 are front and longitudinal section views, respectively, of one embodiment of the plug breaker discharge module
  • Figs. 12 and 13 are sectional end and side views, respectively, of a second plug breaker module, which includes a variable shear penetration into the plug;
  • Figs. 14 and 15 are end and side views, respectively, of a third embodiment of the plug breaker module, which includes axially staggered, variable length pegs for penetration into the plug;
  • Fig. 16 is a longitudinal view of a screw device configured in accordance with the invention and adapted for feeding chip plugs into a chemical impregnation bath;
  • Figure 17 is an end view of an alternative drainage module housing, as viewed axially intermediate the ends;
  • Figure 18 is a view similar to Figure 13, showing the preferred form of the resistance peg and associated adjustment mechanism for the discharge housing.
  • FIG. 1 shows a longitudinal view of a modular compression screw device 10 in accordance with the invention, wherein each of the five main modules is indicated as A, B, C, D, and E.
  • the functions of these modules are well known in the relevant field of technology, but the modular implementation of those functions using adjustable modules whereby the overall characteristics and performance of the device can be matched to a wide variety of end use applications, is considered novel.
  • Module A is a drive module including a drive housing 12, a drive bearing assembly 14 within the drive housing, and a drive flange 16 at one end of the drive housing.
  • the details of the internal configuration of the drive module are not important to the invention, except that at least two, and preferably at least three, different thrust capacities, i.e., low, medium, and high, are available from three distinct, interchangeable drive modules, each of which has a substantially identical drive flange 16.
  • the drive module A has a drive shaft 18 with a free end 20 adapted to be connected to a drive motor or the like (not shown) , and an opposite end which has a shaft flange 22 or the like securable in fixed relation with a mating flange 24 or the like on the screw module D.
  • the screw module D includes a first portion 26 including screw flange 24, connected for rotation to the drive module, and in particular, to the shaft flange 22.
  • the operative portion of the screw includes a shaft 28, which preferably has a straight portion 30, an outwardly tapered portion 32, and another straight portion 34.
  • Screw flights 36 project from the portions 30,32,34 of the screw, in a manner well known in this field of technology.
  • the screw discharge end 35 which has no flights, is supported by a bearing or similar mechanical structure 58, to maintain a central position along the nominal axis of the screw device 10.
  • the feed or stock material enters the screw device 10 through an inlet module B which includes an inlet housing 38, a first inlet flange 40 detachably mated with the drive flange 16, an inlet opening 42 for receiving the stock material into the device, and a second inlet flange 44.
  • One or more processing components C1,C2 define a processor module C having a processor housing 46, and a first processor flange 48 mated with the inlet second flange 44, and a processor second flange 50.
  • the discharge module E includes a discharge housing 52, a discharge flange 54 mated with the processor second flange 50, and means defining an opening 56 for discharging consolidated material from the device.
  • a biased pressure valve (not shown) may optionally be attached to the end module E.
  • the modules B, C and E define a bore for receiving the screw module D and cooperating therewith to process the feed material.
  • the screw module D functions as a unitary piece with the screw flange 24 at the upstream end, a second portion 30 disposed in the inlet module B in fluid communication with the inlet opening 42 for receiving and advancing the stock material toward the processing module C, a third and fourth portion 32,34 disposed in the processing module C for consolidating the stock material by compressing the material against the bore of the processor housing 46, and a fifth portion 35 at least partially disposed in the discharge module E.
  • consolidation should be understood in the most general sense, to mean the bringing together of flowable solids into a more intimate contact with each other, whereby the volume of the material is reduced and the bulk density of the material is increased.
  • consolidation includes the removal of water or liquid in which the solids are suspended in a slurry; the compaction of dry solids such as fibers and chips, into a plug; or the pressurization of solid material to physically break down cellular structure or the like, thereby increasing the solid's density.
  • consolidation can occur as part of a variety of end use applications including dewatering, with or without feeding, compaction, refining, etc.
  • the screw device 10 of Figure 1 is adapted to receive wood chips or similar cellulosic material through the inlet module B, convey the chips toward the right, into the processing module C, where the chips are consolidated as they are conveyed farther to the right by the screw flights 36, and compressed in the space 60 between the increasing taper on the screw shaft 28, and the constant diameter bore 62 of the compression housing 46 (component Cl) of processing module C. Further consolidation occurs in the module drain housing 47 (component C2) of the processing module C.
  • the bores of housings 38,46,47 and 52 of the inlet, processing and discharge modules define a substantially constant screw wall or bore diameter, although breaker bars or the like 49 may optionally project into the bore.
  • one or more of the modules be adjustable so that the device can be optimized for the particular end use application.
  • Adjustability in one sense means the capability to initially fabricate a module component according to standard specifications, and adjust the internals of the component during fabrication of the compression screw device.
  • the second aspect of adjustability is the capability to make such alterations in the field, either during field testing or during normal use when compensation for the effects of wear or a change in feed material should be made.
  • the preferred implementation of the present invention is directed to a screw device having adjustable processing modules C and end module E.
  • the adjustability is primarily with respect to the effective flow cross section of the longitudinal flow bore including the processing bore 62, seal area 64 and discharge opening 56, and can be achieved without removing the screw module D from its normally supported orientation on the device axis, i.e., coaxial with the processing bore 62.
  • the adjustable compression housing component Cl, drainage housing component C2, and the discharge module E will each be described in detail immediately below, with Fig. 2 as a frame of reference.
  • compression component Cl Preferred Compression Housing Component
  • the embodiments of compression component Cl will be identified with the number series 100 as shown in Figures 2-6, and may be used either in a modular device as described herein and shown in Figure 2, or as an integral part of other plug screw feeders and the like to overcome - li ⁇
  • the material must be compressed enough to form a steam seal or pressure type plug, but the plug must be loose enough to allow continuous conveying to occur.
  • the screw device operates in a narrow band. If the compression of the material is too high the plug screw will draw excessively high motor loads and possibly stall. If the compression of the material is too low a gas type seal cannot be maintained. Often, slight variations in the bulk material properties will move the operation of the plug screw feeder outside its narrow band, resulting in blowback or stalled conditions. Since these devices are used in continuous process systems, any interruption in their continuous operation can disrupt the functioning of an entire plant.
  • the unit When a problem develops with a plug screw feeder, the unit is usually immediately disassembled and parts are modified either by machining or by building up various regions of the housings or screw in an attempt to alter the compression ratio. Since this is a trial and error procedure it can become a very time consuming and costly undertaking to fine tune a unit for a particular feedstock, particularly when this must be done in the field.
  • the invention includes a set of casings 102 which surround the compression screw portion 32, and removable liners 104 which can be changed to either reduce or increase the total compression ratio of the unit.
  • the casings 102 can either be segments of a cylinder, to be used in conjunction with uniform screw flights which would have an increasing shaft diameter; or the casings can be segments of a cone, to be used in conjunction with tapered screw flights.
  • the casings 102 form the component housing to contain the internal pressure developed by the compression of the conveyed material.
  • the liners 104 are provided in thicknesses varying by approximately 1/8 inch increments. The varying thickness of the liners 104 allow the effective cross-sectional area of the screw bore to be changed, which results in a change in the overall compression ratio of unit.
  • the liners 104 also function to resist wear.
  • Having a plug screw feeder installed in the field with removable housing liners greatly simplifies fine tuning the compression ratio in the field. For example, assume a plug screw feeder unit was installed to convey wood chips into a high pressure refining system. At the installation assume the chip moisture content was lower than expected, resulting in high plug screw feeder motor loads and intermittent stall conditions. Correcting this situation would require reducing the the compression ratio of the unit. With removable liners this is accomplished in the following manner. The split casings 102 are taken apart along flanges 106, the installed liners 104 are removed and a spare set of thinner liners are put in place. For example, reducing the bore of the liners by 1/4 inch on the radius would result in reducing the compression ratio by approximately 19%.
  • the casings may be directly or indirectly connected to end flanges 108, which, if present, may or may not require removal and reattachment to the remainder of the screw device.
  • the replacement in accordance with the invention can be accomplished within about an hour as compared to a minimum of 24-36 hours required to change the compression ratio conventionally by machining either the screw or the bore of the housings.
  • any compression type screw device to convey material the material must be prevented from rotating with the screw 32.
  • the frictional resistance radially in the surrounding compression wall must be greater than the frictional resistance of the screw flights and shaft.
  • Conventional plug screw feeders normally have a series of grooves either cast or machined into the housings for this purpose.
  • the present invention does not utilize a series of grooves or bars in the housing, but rather anti-rotation bars 110 are sandwiched between the adjacent casings 102.
  • the anti-rotation bars 110 protrude radially beyond the inner surface 112 of the liners 104 by a minimum of 1/4 inch.
  • the radially inward projection height of the bar 110 increases as the thickness of the liners decreases. The distance from the inner edge 114 of the bar 110 to the outer diameter edge 116 of the screw flight would be held constant.
  • a screw press housing 100 defines a substantially cylindrical or axially tapered first bore 118 for coaxially receiving a screw 32.
  • the housing 100 is formed by connecting together a plurality of axially elongated casing members 102 , each casing member in cross section having an inner, concave surface 120 which defines an arc segment having a first circumferential span and a first radius of curvature, and an outer surface 122 defining the exterior of the housing 100.
  • Fixture means such as shoulders or flanges 106, extend radially from the ends of each segment, for attaching together adjacent casing members, whereby the inner surfaces 120 of the connected casing members form a first substantially cylindrical or conical bore 118.
  • a plurality of bar members 110 are situated respectively between the flanges 106 of two attached casing members 102.
  • the bars have an inner edge 114 that extends radially inward into the first bore 118, toward the housing axis 124.
  • An axially elongated liner member 104 is coaxially retained within the first bore 118 and, when viewed in cross section, has substantially the same circumferential span as its associated casing member 102.
  • the liner may optionally be split and overlapped as at 126 to assure a good fit.
  • the outer wall 128 of a given liner is supported radially by the associated casing member.
  • the inner wall 112 of each liner member has a second radius of curvature smaller than the first radius but is large enough to ensure an annular gap 132 relative to the screw flights 36 that operate in substantially the same plane as the given cross section.
  • the circumferential ends 134,136 of each liner are juxtaposed with the respective bar member 110.
  • the inner edge of each bar member 114 extends radially closer toward the housing axis 124 than do the liner inner walls 112, e.g., the distance between the edges 114 of diagonally opposed bars is only slightly larger than the screw flight diameter.
  • adjustment bolts 138 threadedly pass through the casing members 102 and can either engage mating threads in the liner 104 or merely provide stops surfaces, so as to adjust the radial limit position of the liner relative to the casing member.
  • the replaceable liners 104 can extend the entire length of the housings or optionally can be positioned only in the high compression zone, near the end of the screw.
  • the screw bore of the housing can be defined partly by the liner inner walls and partly by the inner surfaces of the casing members.
  • the casing members need not have the same material thickness or radii of curvature.
  • the inner surface of the casing member may have a radius of curvature that is the same as, greater than, or less than the radius of curvature of the inner wall of the liner member.
  • the liners situated in two of four casing members may optionally be in the form of screen plates 142 which have drain holes 144 formed therein.
  • the bar members 146 may be formed with radially extending drainage slots 148 by which extracted liquid can flow to the housing exterior and into an affluent drain basin or the like when the screw rotates in the direction of the arrow.
  • a spacer or auxiliary liner 150 may be provided between screen plate 142 and the inner surface of casing 152 to facilitate drainage.
  • the casing members 152' which surround the screen plates 142 may optionally be formed so as to define a series of axially spaced apart ribs 156 with relatively large openings 154 therebetween.
  • the supporting ribs 156 support the inner screen plate 142 directly, or as shown, indirectly through the intervening auxiliary liner 150 which also has drain holes therein.
  • the ribs 156 do not have drain holes, however, the large spacings 154 between each rib provide ample room for drainage to take place.
  • the embodiment 160 shown in Figures 5 and 6 is another alternative.
  • the recessed sections 162 with liners 164 do not have drainage holes whereas the non-recessed sections 160 do have drainage holes 172.
  • Providing drainage holes 172 close to the screw outer diameter prevents a build-up of material over the holes, which would impede liquid flow.
  • the screw flights keep the holes 172 wiped clean, while the liners 164 in the recessed sections still enable the compression ratio of the unit to be changed.
  • a plug screw feeder of the type shown in Figure 3 does not have drain holes and is used for feeding dry material into a pressurized zone. In other instances, where wet chips are being conveyed, it is necessary to provide drain holes in order for the unit to function properly. Moreover, it is clear that when a compression screw is being used specifically as a drainage press, drainage holes or openings must be present. It is within the skill of an ordinary practitioner in this art to combine the various features shown in Figures 3-6 for the particular end use application.
  • the anti-rotation bars at the casing junctures eliminate the need to have grooves or bars in the housing surfaces, and therefore the wear liners can be one piece, rolled plates. Once assembled, the anti-rotation bars secure the wear liners in the housing and prevent them from sliding or rotating with the material in the tangential direction.
  • This arrangement provides the maximum width of an anti-rotation groove.
  • the shear area or the wood imbedded in the groove is at a maximum, and therefore the required frictional resistance of the screw flights and screw shaft surface must be much higher before plug rotation occurs, as compared to the conventional use of smaller width grooves.
  • the screw bore can be increased by decreasing the thickness of the wear liners, however the clearance between the anti-rotation bars and the outside diameter screw flights can be maintained.
  • the clearance between the O.D. of the screw flight and the I.D. of the housing or anti-rotation bar imbedded in the housing would increase, resulting in less effective resistance to plug rotation.
  • the second component which is preferably adjustable in the processing module C is the drainage component C2 as indicated at 200 in Figure 2.
  • screw presses which are used to drain fibrous materials generally use split housings with drainage holes or axial slots to drain water away from the material as it is compressed within the housings.
  • High compression units generate enough internal pressure that it is often necessary to support the perforated housing or the slotted housing sections with support ribs.
  • a popular construction of high pressure units consists of bars placed axially along the length of the screw, assembled with a slight clearance between each bar. This configuration results in drainage slots along the length of the screw. The bars are held in place and supported by a heavily ribbed set of cages which when bolted together completely surround the compression screw.
  • the housing must be a split design for assembly reasons, but this weakens the housings since the split results in the ribs being loaded as curved beams with restrained ends at the bolted joints.
  • the ribs must have a heavy thickness and deep cross-section, so the cost of the drain bars and supporting ribbed housings is high.
  • Such housings require extensive machining and each individual bar must be ground to fit properly in the assembly.
  • the details of new drainage housing 200 in accordance with the invention are shown in Figures 7-9.
  • the housing is made from a plurality of rings 202 generally 3/8 inch to 1/2 inch thick which are assembled in a stack.
  • the gap 204 between the individual rings is set by shims 206 placed over the assembly bolts 208 which extend through the entire stack of rings and clamp the assembly together by drawing the rings toward each other.
  • the gap between the individual rings generally ranges from .010 inch to .040 inch.
  • the inside diameter 210 of the rings is slightly larger than the outside diameter of screw flights passing therethrough.
  • Two diametrically opposed grooves 214 are machined in each ring, resulting in slots 215 extending the length of the stacked assembly.
  • Positioned in each slot is an anti-rotation bar 216, the longitudinal ends 218 of which are secured with bolts 220 which pass through radial holes in the end support plates 222 (only one shown) .
  • the purpose of the thick end support plates 222 is solely to provide bolting for the anti-rotation bars 216.
  • the anti-rotation bars 216 when positioned in the slots 215 protrude radially inward from the inside diameter of the rings, by approximately 1/4 inch to 3/8 inch, along the axial length of the inner surface 210.
  • the rings 202 preferably do not have a constant thickness along their full radial distance. Approximately 1/4 inch away from the inside diameter 210 of the rings, the front surface 224 of each individual ring is recessed back approximately 1/16 inch. The recessed area 226 of each ring is intended to prevent fines which may pass through the grooves 214, from building up in the rings and impeding drainage.
  • a set of opposed notches 228 are positioned 90 degrees out of alignment with the inside grooves 214.
  • the outside notches 228 fit over side bars 230 which act as a brace for the ring assembly and provide torque resistance to the unit.
  • the side bars 230 are part of a frame that is rigidly connected to the supporting base 232 of the machine.
  • this aspect of the invention is directed to a compression screw device having a drain housing 200 including a screw bore 234 for coaxially receiving a rotating screw and a frame or base 232 for supporting the housing.
  • the housing comprises a plurality of substantially annular rings 202 rigidly stacked together along the housing axis 236, each ring having an inner profile 210 defining a substantially circular opening in alignment with the openings with the other stacked rings to form the screw bore 234.
  • the outer profile 238 of the annulus includes means 228 for engaging the frame, preferably in the form of two diametrically opposed notches which are horizontally oriented relative to the assembled screw device.
  • the frame of the screw device has an elongated, rigidly supported horizontal brace bar 230 having a profile which dovetails with the notches on the stacked rings, thereby resisting torque loads imposed by the rotating screw within the screw bore.
  • Spacer means 206 are interposed between each ring 202, for defining a drainage channel or gap 204 which extends substantially 360° radially from the screw bore to the outer profile where the expressed liquid is collected and drained away.
  • the stacked rings are preferably drawn toward each other so as to be compressed against the respective shims, by a plurality of bolts 208, for example four, which pass through a respective plurality of uniformly spaced holes 242 in the solid annulus of each ring.
  • FIG. 17 An alternative embodiment of the drainage component, having individual features which may optionally be incorporated into the embodiment described immediately above, is shown as 250 in Figure 17.
  • an outer shell 252 having upper and lower portions defines a collection volume where the drained fluids are accumulated and removed.
  • the drainage rings 260 are confined between axially spaced apart end plates or flanges 254 (only one of which is shown in Figure 17) , the outer diameter of which defines an annular gap 256 with the shell 252.
  • the rings 260 do not have holes for receiving the tensioning bolts, but rather the tensioning bolts 258 span the opposed flanges 254 which, when drawn toward each other, tightly pack the individual rings 260.
  • Each ring 260 has a substantially circular outer diameter 262 less than the diameter of flange 254 and a substantially circular inner diameter 264, except that the inner diameter has at least one, preferably two diametrically opposed, integrally formed anti-rotation projections 266. These projections 266 are preferably thicker in the axial direction, than the annular body portion 268 of ring 260.
  • a plurality of integrally formed shim portions or regions 270 are also formed on and thicker than the annulus 268, preferably the same thickness as the protrusions 266. In the illustrated embodiment, two integral shims 270 are spaced apart in each quadrant.
  • the rings 260 are aligned so that the protruding anti-rotation projections 266 and the integral shims 270 are in registry in the axial direction, with corresponding structures on all rings in the stack.
  • the inner diameter 264 of the ring includes a substantially circular recessed drainage gap 272 as in the previously described embodiment.
  • the raised or thickened regions defining the integral shims 270 substitute functionally for the individual spacers or shims 206 for establishing the width of the drainage channel such as 204 shown in Figure 7.
  • the raised surfaces on integral shims 270 are ground to a thickness which when in contact with the adjacent ring in the stack, establishes the desired drainage channel radially along the body portions 268. This feature of the embodiment shown in Figure 17 would be used when the required drainage channel is known with substantial certainty for a particular process.
  • An advantage of the integral shim embodiment for setting the size of the drainage channel is that it eliminates a large number of separate shims and thereby simplifies the assembly of the press.
  • the integral projections 266 shown in Figure 17, provide the functional equivalent to the anti-rotation bars 216 in the embodiment of Figure 7.
  • the protrusions 266 line up with one another in the axial direction to form what are essentially anti-rotation bars along the full axial length of the ring stack. This reduces cost by eliminating the thick plates at 222 at each axial end of the stack, the separate anti-rotation bars, and the required machining associated with that arrangement.
  • the size of the drainage rings in the embodiment of Figure 17 can be reduced relative to that of Figure 7, by the feature of arranging the tensioning bolts 258 at the outer diameter 262 of the stack of rings.
  • the rings are supported and positioned by the frame members 232,230 via notch 274 in the outer diameter 262 of each ring, as in the embodiment of Figure 7.
  • the tensioning rings 258 serve only the single function of drawing the rings toward each other.
  • the outside diameter 262 of the rings can be reduced relative to the embodiment of Figure 7, because the annulus 268 does not carry the holes 242.
  • the thickness of annulus 268 need only be sufficient to support the applied loading which consists of the internal pressure, the torque, and the axial friction forces produced as the processed material is being conveyed through the unit. Eliminating the unnecessary depth of the annulus 268 reduces material costs, makes the pieces easier to manufacture, and keeps the weight of individual rings low enough so that one person can lift them.
  • a solid ring can withstand much higher internal pressure than a split housing, simply because the ring is loaded in hoop stress tension, whereas a split housing is basically a curved beam with large bending moments at the split joint.
  • the individual rings 202 are assembled in the field by sliding them over the side support bars 230 and the clamping bolts 208 while the discharge end module is detached.
  • the gap 204 between each individual ring can be adjusted slightly by changing the shims 206 placed over the clamping bolts without removing the rings from around the screw.
  • the screw remains in the longitudinal bore during axial adjustment of the rings. Compensation for the accumulated length due to large changes in the individual gap requires removal of the discharge module and is accomplished by adding or deleting rings as necessary and assembling the compensation shims at the upstream end of the stack to compensate for any variances in overall length of the assembly.
  • the stacked ring arrangement eliminates the use of supporting rib cages, which greatly reduces the overall cost of the unit. Assembly time is also reduced as compared to the use of the screen bars and cage arrangement.
  • the assembly required for the conventional bar/ribbed cage assembly consists of positioning each drain bar in place, shimming between the top drain bars and the clamp bars bolted to the split face of the cage, and then placing the assembled units around the screw and bolting them in place. If the drain bars are not precisely and tightly held in place, a tight plug of material can lift up and dislodge the corner of one bar, and cause all the other drain bars to dislodge as they all become loose.
  • the solid rings of the present invention are self contained and cannot come apart except by complete fracture of a ring or failure of the clamp bolts.
  • the modular screw device of Figure 2 preferably includes, as the discharge module E, a plug breaker component 300 of the type shown in Figures 10-15.
  • Any compression screw used for dewatering or forming a gas seal in a continuous feeding operation functions by mechanically squeezing or compressing the material being conveyed. This is done by reducing the cross-sectional area of the screw flight and/or reducing the screw pitch.
  • cohesive material such as wet wood chips or fiber are handled in a high compression screw, the material often discharges as a hard, dense plug which breaks off into variously sized lumps. The non-uniform lumps adversely affect processing downstream from the compression screw.
  • plug spinning becomes more of a problem because the squeezed out liquid travels to the outside diameter of the screw. This can result in a lower friction coefficient at the screw outside diameter than against the screw shaft.
  • the particles against the screw shaft adhere to the shaft surface as they become dryer, and the outer particles against the housing bore begin to slide over one another more easily as they become lubricated with the liquid being expressed toward the housing walls. This condition often causes the plug to rotate with the screw, whereupon conveying will cease.
  • the overall object of the preferred end module 300 is to accomplish the three above-mentioned tasks. These are to break up the plug, provide maximum anti-rotation of the plug in the high compression zone, and provide a bearing support for the discharge end of the screw.
  • the fourth task of adjusting the cross sectional flow area permits adjustment of the compression in an upstream component.
  • the basic plug breaker end module 300 shown in Figures 10 and 11 comprises a tubular outer housing 302 which bolts directly to the downstream end of the screw housing or processing module such as 200.
  • An internal cup-like bearing 304 is situated on the housing axis 306.
  • the bearing 304 is supported by longitudinal plates 306 that have one end 308 welded to the inside diameter of the outer housing 302 and the other end 310 welded to the outside diameter of the bearing member 304.
  • the plates 306 are welded tangentially to the bearing member 304 so that in use, the plates are loaded in tension or compression rather than in bending as would arise from a tendency for plug rotation to take place under high compression conditions.
  • the axially extending plates 306 function as knife edges against the passing compressed plug, creating a nonuniform chip velocity. This nonuniform velocity develops shear forces within the plug, which break up the lumps as they discharge from the plates. The shear forces in the particle-to-particle movement within the segments of the plug passing through the plates, also helps fiber
  • the bearing member 304 is lubricated by water which travels through a bore 312 drilled through one of the breaker plates 306 from the outside wall of the component housing 302 to the closed end 314 of the bearing.
  • the water not only lubricates, but also flushes the bearing, keeping fines out of the area and prolonging the life of the bearing.
  • the discharge end housing is thus in the form of a substantially tubular housing 302 having a cylindrical wall 316 defining a bore with a longitudinal axis 306 and upstream and downstream, preferably flanged ends 318,320.
  • the upstream or forward portion 322 of the bore is adapted to receive the substantially cylindrical end portion of the screw, i.e., a cylinder having no screw flights.
  • the downstream internal portion 324 of the bore has a plurality of breaker plates 306 rigidly depending from the bore wall 316.
  • the plates are oriented so that the substantially planar opposed sides 326,328 defining the longitudinal and height dimensions, extend substantially parallel with the axial flow direction of the material conveyed by the screw, whereas the cross sectional thickness dimension 330, which confronts the oncoming material, is relatively thin, i.e., the frontal area of the plate is less than the area of either side.
  • a bearing member 304 in the form of a cylindrical cup is centered coaxially within the housing, so that the open end thereof rotationally supports an axially extending stem portion of the screw.
  • the breaker plates preferably four in number, are rigidly connected substantially tangentially to the bearing member.
  • wood chips are chemically impregnated.
  • the chemicals which are impregnated into the chips helps to partially break down the chips into fibers and to bleach the wood material.
  • Wood chips are impregnated in the following manner.
  • the chips are compressed in a compression screw device. This squeezes out any undesired liquid imbedded into the chips. As the compressed chips discharge from the screw device, they expand almost back to the original volume. If this expansion takes place with the wood submersed in a chemical liquor, the liquor is drawn into the voids and crevices of the chips much the same way a squeezed sponge upon being allowed to expand will absorb water. In this manner, chemicals which contribute to the pulping process can be impregnated or drawn into the voids and crevices of the chips.
  • a way to maximize the chemical uptake and optimize the process is to partially separate and open up the chips so that more fiber surface is exposed to the chemicals and the chemicals penetrate uniformly through the chips.
  • Plug breaker of the type shown in Figs. 12-16 with added radially adjustable resistance pegs or bolts, helps to optimize the impregnation process in a very cost-effective and efficient manner.
  • Plug breaker discharge housings 350 and 380 provide variable axial resistance to chip flow.
  • the module 350 in Figs. 12 and 13 has a tubular housing 352, centrally located bearing member 354, and bearing support plates 356 which extend horizontally in opposite directions between the bearing member 354 and the housing 352.
  • the support plates 356 extend the full axial length of the housing and are tapered at the upstream end to facilitate the other function of breaking up the material as it flows through the cross sectional area 364 transverse to the housing axis.
  • two vertically aligned resistance pegs or bolts 360 pass in threaded engagement through bosses 358 in housing 352, whereby the projecting end 362 of each bolt 360 penetrates into the cross sectional area 364 a variable distance that is adjustable externally of the housing.
  • the pegs 360 are located in and supported by the housing 352, upstream of the outlet opening 351.
  • the discharge end module 350 differs from the module 300 shown in Figs. 10 and 11, not only with respect to the adjustable resistance bolt or peg, but also in the geometric relation to the screw. As shown in Fig. 1, only the stem 58 of the screw enters the discharge module 350, whereas the large, cylindrical trailing end of the shaft immediately upstream of the stem 58, enters the forward portion 322 of the end module 300.
  • the bearing support and breaker plates 306,356 of end modules 300,350 respectively, impede the axial flow of a plug of chips through the upstream components of the unit, thereby contributing to chip compression. Adding the pegs or bars to the cross section of the discharge housing in accordance with the configuration of end housing 350, further adds to impeding the chip flow.
  • FIG. 14 and 15 another embodiment of the discharge module 380 is shown in Figs. 14 and 15.
  • the housing 382, bearing member 386, and plates 384 are substantially identical with the corresponding structure 352,354,356 of the embodiment shown in Fig. 12, except that six, rather than two, adjustable pegs are provided.
  • four bolts 388,390 are provided at 90° intervals in the same imaginary plane transverse to the housing axis, whereas two adjustable pegs 392 are provided in 180° opposition through a plane that is offset axially downstream.
  • the radial adjustability of the pegs not only alters the amount of chip compression in the unit, but the protruding pegs also produce a shearing action on the chip plug as the material passes in and around the pegs. This shearing action effectively opens the chips, exposing the chip interior exactly when expansion begins to take place as they discharge from the plug breaker into, e.g., the chemical liquor of a downstream component.
  • manual adjustment of the pegs is shown, it would be well within the skill of practitioners in this art to mechanize and automate the peg adjustment as part of a process control system for on-line adjustment while the system is running.
  • Figure 18 illustrates one implementation of a production arrangement for adjusting the resistance peg in the discharge module 350', which, in other respects, is similar to the embodiment 350 shown in Figures 12 and 13. It should be appreciated, however, that the adjustment mechanism shown in Figure 18 can be used with other embodiments as well.
  • a smooth peg 353 made from an abrasion resistant material is situated in smooth bore 367 in boss 358, immediately downstream of the upstream flange housing 352.
  • a positioner plate 355 overlies boss 358, and has a smooth bore 375 and a threaded bore 373 for receiving anchor bolt 369 and adjustment bolt sleeve 357.
  • Anchor bolt 369 passes through bore 375 into threaded engagement with bore 371 in the boss.
  • the sleeve 357 is secured by nut 359 at the upper surface of plate 355.
  • control rod 361 carries a pin 363 for attachment to the peg 353.
  • the control rod 361 slides vertically through sleeve 357 under the direction of a controller. In this fashion, the extent of the projection of the peg 353 into the flow area of the discharge housing 350' is adjustable.
  • an improved screw device may include one or more of the compression housings 100, 140, or 154; drainage housing 200; or discharge housings 300, 350, or 380.
  • Fig. 16 illustrates a screw device configuration 700 having only one processing module, the drain housing 200, coupled with the end housing 380, to form a dewatering press used as a plug screw feeder into a chemical impregnation component (not shown) .
  • a chip inlet module 400 is connected to the drain module 200
  • a drive module 500 is connected to the inlet module 400, for driving a unitary screw 600 that has an increasing taper and full flights within the drain housing 200.
  • MSD modular screw device
  • a comparably configured screw device including a processing module available from Andritz Sprout-Bauer, Inc. , Muncy, Pennsylvania, as the Model 560 Pressafiner component.
  • a comparative chemical impregnation trial with aspen wood was made, with the important result that the MSD incorporating the drain housing 200 and discharge housing 380 of the present invention, produced approximately a 50% higher chemical uptake than the Pressafiner configuration.
  • the MSD also had slightly less fines in the effluent than the Pressafiner configuration. Fiber classifications at comparable freeness were essentially equal.
  • the MSD had a 2-1 compression ratio.
  • the Pressafiner configuration was assembled with a standard 4 to 1 combination of worms and collars. The impregnation was in both instances, accomplished in two stages. In the first impregnation stage, all adjustable pegs were set at 5/8" extension into the discharge bore. On the second impregnation stage, all pegs were advanced into a 1-1/4" extension into the plug. This change was easily accomplished from outside the housing without removing the discharge module 380 from the processing module 200, by manually turning the pegs (bolts) to the desired depth. In a production mode, this penetration is preferably achieved with an automatic compression control system 394 for effecting peg movement from outside the housing.
  • the results of this comparative experiment showed that the combination of the stacked ring drainage housing 200 and the adjustable plug breaker discharge housing 380, produce drainage and chemical uptake for effective chemical impregnation.
  • the one-piece screw 600, stacked ring drainage housing 200, and plug breaker discharge module 380 permit significant cost savings in construction relative to the Pressafiner configuration which has worms and collars, composite shaft, and a drainage component consisting of conventional cages and bars.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Treatment Of Sludge (AREA)

Abstract

Dispositif à vis modulaire (10) comportant au moins un élément de logement de processeur (100, 104, 160, 200, 250) ou un élément de logement de décharge (350, 350', 380) pouvant être modifié afin de régler les caractéristiques de compression ou de drainage du dispositif. Les logements de compression (100, 140, 160) sont réglables par changement des chemises (104, 142, 150, 164), les logements d'évacuation (200, 250) sont ajustables par réglage de l'écartement entre une pluralité d'anneaux empilés axialement (202, 260), et les logements de décharge (350, 350', 380) sont réglables au moyen de chevilles ou de boulons (353, 362, 388, 390, 392) mobiles radialement dans l'alésage d'écoulement en amont de l'ouverture de décharge. Qu'il soit réglable ou non le logement de décharge (300) comprend de préférence un organe de support central (310) destiné à porter la vis ainsi que les plaques (306) éliminant les bouchons, s'étendant entre la paroi du logement (322) ainsi que l'organe de support.
PCT/US1992/000939 1991-02-12 1992-02-06 Dispositif a vis et elements de compression reglables WO1992013710A1 (fr)

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US65473191A 1991-02-12 1991-02-12
US654,731 1991-02-12

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Cited By (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6145766A (en) * 1997-02-14 2000-11-14 Andritz-Patentverwaltungs-Gesellschaft M.B.H. Screw device for dewatering and defibrating ligno-cellulose material
US6899791B2 (en) 1997-08-08 2005-05-31 Andritz Inc. Method of pretreating lignocellulose fiber-containing material in a pulp refining process
WO2005063475A2 (fr) * 2003-12-23 2005-07-14 Extruconsult Extrudeuse et procede de fonctionnement associe
EP1568478A1 (fr) 2004-02-26 2005-08-31 VM Press S.r.l. Machine de compactage de déchets
EP1992894A1 (fr) * 2007-05-14 2008-11-19 Pallmann Maschinenfabrik Gmbh + Co. Kg Dispositif de séchage par compactage de matériaux de chargement fluides ou en vrac
WO2011036301A1 (fr) * 2009-09-28 2011-03-31 Few Separator Gmbh Système de montage de tamis pour un séparateur à vis à pression et séparateur à vis à pression muni d'un tel système de montage de tamis
EP2561981A3 (fr) * 2011-08-26 2013-12-25 Thöni Industriebetriebe GmbH Convoyeur à vis
EP2937210A1 (fr) * 2014-04-22 2015-10-28 Rio Tinto Alcan International Limited Presse à vis avec plaques filtrantes
EP2833986A4 (fr) * 2012-04-05 2016-04-20 Greenfield Specialty Alcohols Inc Presse d'extrusion à double vis pour la séparation solide / fluide
US9352253B2 (en) 2010-11-09 2016-05-31 Greenfield Specialty Alcohols Inc. Solid/fluid separation device and method for treating biomass including solid/fluid separation
AT518983A4 (de) * 2016-12-02 2018-03-15 Andritz Ag Maschf VORRICHTUNG ZUM ENTWÄSSERN VON SCHÜTTFÄHIGEM ODER FLIEßFÄHIGEM AUFGABEGUT
DK179335B1 (en) * 2014-04-22 2018-05-14 Rio Tinto Alcan Int Ltd Modular screw press
AT16471U1 (de) * 2017-08-22 2019-10-15 Voith Patent Gmbh Schneckenpresse
US10786763B2 (en) 2016-05-02 2020-09-29 Greenfield Specialty Alcohols Inc. Filter for extruder press
EP3843984A4 (fr) * 2018-08-31 2022-03-16 Valmet Ab Distributeur à vis et tuyau à utiliser dans un distributeur à vis

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US1902738A (en) * 1927-09-02 1933-03-21 Henry W Tuttle Machine for expressing fruit juices and the like
US3288056A (en) * 1965-04-05 1966-11-29 Bauer Bros Co Iris type valve
US3695173A (en) * 1972-01-28 1972-10-03 Clyde Harold Cox Sludge dewatering
US4429551A (en) * 1982-04-29 1984-02-07 Hoshizaki Electric Co., Ltd. Auger type icemaker

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1902738A (en) * 1927-09-02 1933-03-21 Henry W Tuttle Machine for expressing fruit juices and the like
US3288056A (en) * 1965-04-05 1966-11-29 Bauer Bros Co Iris type valve
US3695173A (en) * 1972-01-28 1972-10-03 Clyde Harold Cox Sludge dewatering
US4429551A (en) * 1982-04-29 1984-02-07 Hoshizaki Electric Co., Ltd. Auger type icemaker

Cited By (21)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6145766A (en) * 1997-02-14 2000-11-14 Andritz-Patentverwaltungs-Gesellschaft M.B.H. Screw device for dewatering and defibrating ligno-cellulose material
US6899791B2 (en) 1997-08-08 2005-05-31 Andritz Inc. Method of pretreating lignocellulose fiber-containing material in a pulp refining process
WO2005063475A2 (fr) * 2003-12-23 2005-07-14 Extruconsult Extrudeuse et procede de fonctionnement associe
WO2005063475A3 (fr) * 2003-12-23 2005-08-11 Extruconsult Extrudeuse et procede de fonctionnement associe
EP1568478A1 (fr) 2004-02-26 2005-08-31 VM Press S.r.l. Machine de compactage de déchets
EP1992894A1 (fr) * 2007-05-14 2008-11-19 Pallmann Maschinenfabrik Gmbh + Co. Kg Dispositif de séchage par compactage de matériaux de chargement fluides ou en vrac
WO2011036301A1 (fr) * 2009-09-28 2011-03-31 Few Separator Gmbh Système de montage de tamis pour un séparateur à vis à pression et séparateur à vis à pression muni d'un tel système de montage de tamis
US9352253B2 (en) 2010-11-09 2016-05-31 Greenfield Specialty Alcohols Inc. Solid/fluid separation device and method for treating biomass including solid/fluid separation
EP2561981A3 (fr) * 2011-08-26 2013-12-25 Thöni Industriebetriebe GmbH Convoyeur à vis
EP2833986A4 (fr) * 2012-04-05 2016-04-20 Greenfield Specialty Alcohols Inc Presse d'extrusion à double vis pour la séparation solide / fluide
US9643110B2 (en) 2012-04-05 2017-05-09 Greenfield Specialty Alcohols Inc. Twin screw extruder press for solid/fluid separation
DK179335B1 (en) * 2014-04-22 2018-05-14 Rio Tinto Alcan Int Ltd Modular screw press
CN106232200A (zh) * 2014-04-22 2016-12-14 力拓艾尔坎国际有限公司 具有过滤板的螺杆压力机
EP3134193A4 (fr) * 2014-04-22 2018-01-10 Rio Tinto Alcan International Limited Presse à vis avec plaques de filtre
EP2937210A1 (fr) * 2014-04-22 2015-10-28 Rio Tinto Alcan International Limited Presse à vis avec plaques filtrantes
US10786763B2 (en) 2016-05-02 2020-09-29 Greenfield Specialty Alcohols Inc. Filter for extruder press
AT518983A4 (de) * 2016-12-02 2018-03-15 Andritz Ag Maschf VORRICHTUNG ZUM ENTWÄSSERN VON SCHÜTTFÄHIGEM ODER FLIEßFÄHIGEM AUFGABEGUT
AT518983B1 (de) * 2016-12-02 2018-03-15 Andritz Ag Maschf VORRICHTUNG ZUM ENTWÄSSERN VON SCHÜTTFÄHIGEM ODER FLIEßFÄHIGEM AUFGABEGUT
AT16471U1 (de) * 2017-08-22 2019-10-15 Voith Patent Gmbh Schneckenpresse
EP3843984A4 (fr) * 2018-08-31 2022-03-16 Valmet Ab Distributeur à vis et tuyau à utiliser dans un distributeur à vis
US11919269B2 (en) 2018-08-31 2024-03-05 Valmet Ab Screw feeder

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