Field of the Invention This invention relates to the field of apparatus for compressing loose materials, which may be loose fibrous materials, for introduction as a feedstock in a process occurring at elevated pressures.

Background of the Invention

A number of industrial processes involve the introduction of a loose solid feedstock into a pressurized reaction chamber or vessel. Unless the process is limited to batch operation this may require that the feedstock be pressurized and forced into the reaction vessel while the reaction vessel is maintained at elevated pressure, and possibly also while maintained at elevated temperature. In a continuous process with a pure liquid or a compact solid this may be relatively straightforward. Even for a slurry, or for two- phased flow where solids are suspended in a carrier fluid, this may be possible without undue difficulty. However, the compaction and pressurization of a rather porous, substantially dry solid, which may have the form of chips or flakes, or strands, may present a challenge. For example, these flakes or chips may be ligneous by-products of a forestry or agricultural activity. Earlier attempts to address this challenge are shown and described, for example, in US Patent 4,119,025 of Brown, issued October 10, 1978; US Patent 4,947,743 of Brown et al, issued August 14, 1990; and PCT Application PCT/CA99/00679 of Burke et al., published as WO 00/07806 published February 17, 2000, the subject matter of all of these documents being incorporated herein by reference. At the end of the process, the loose, fibrous, typically organic material leaves the reaction chamber through a discharge assembly of some kind, whence it is collected for further use or processing. To the extent that the process feedstock is then to be used as an input to a subsequent process, such as a biological digestion process, it may be desirable that the fibrous material be finely expanded.

Summary of the Invention In an aspect of the invention there is a power transmission apparatus for a compression stage in a compressor for loose packed materials. The compressor has a first compression stage and a second compression stage. The power transmission apparatus includes a compressor piston of the second compressor stage. The compressor piston is shaped to extend about at least a portion of the first compression stage and to be reciprocally movable with respect thereto. The compressor piston having a first end and a second end. The first end of the compressor piston is an output end thereof, and is shaped to conform to a co-operating mating cylinder within which the compressor piston is mounted to reciprocate in a longitudinal direction. The second end is distant from the first end. The power transmission apparatus having a movable power input interface at which motive force is applied to the compressor piston. The power input interface has a fixed position relative to the first end of the compressor piston. The power transmission apparatus has a stationary reaction datum. The compressor piston is movable in longitudinal reciprocation relative to the stationary reaction datum. The power input interface is driven along a single degree of freedom of motion relative to the stationary reaction datum.

In another feature of that aspect of the invention, the power transmission is free of slack between the power input interface and the first end of the compressor piston. In a further feature the power transmission apparatus includes an actuator cylinder arrangement that includes at least a first actuator cylinder. The stationary reaction datum is defined by a first end of the first actuator cylinder; and the power input interface is defined at least in part by the first actuator piston operating within that first actuator cylinder. In yet another feature, when viewed perpendicular to the longitudinal direction, the compressor piston is located in an intermediate position relative to the actuator cylinder arrangement. In still another feature, the actuator cylinder arrangement includes a plurality of actuator cylinders arrayed in substantially balanced spacing about the compressor piston. In a yet further feature the compressor piston has a body extending between the first and second ends thereof, and has an outwardly extending flange mounted externally thereto. The outwardly extending flange defines at least a portion of the first actuator piston.

In still yet another feature the compressor piston has an externally extending peripheral wall, the wall fits in co-operating relationship within the first actuator cylinder, and the wall has at least a first face positioned in opposition to the stationary reaction datum, and the wall defines the first actuator piston. In another further feature the compressor piston has a bore formed longitudinally therethrough to accommodate the first compression stage. The first actuator cylinder, the first face of the externally extending peripheral wall of the compressor piston, the first end of the compressor piston and the bore formed in the compressor piston are all circular in cross-section and concentric.

In still yet another feature of any of the forgoing aspects and features, the first compressor stage includes a screw compressor mounted concentrically within the piston.

In again another feature of any of the foregoing aspects and features, the compressor piston is annular and has an axially extending passage formed therethrough to accommodate the second compression stage.

In another aspect of the invention there is a power transmission apparatus for a compression stage in a two stage compressor for loose-packed solids. The power transmission includes a compressor piston, a head, and a plurality of power transmission members. The compressor piston is shaped to extend about members of another compression stage and to be reciprocally movable with respect thereto in a longitudinal direction. The piston has a first end and a second end. The second end of the piston is rigidly mounted to the head in a fixed orientation. The first end of the piston is longitudinally distant from the head and is shaped to co-operate with a mating cylinder. The power transmission members is mounted to the head and restricting the head to motion along a fixed reciprocation path in a fixed orientation relative to that reciprocation path. The power transmission members each is mounted to a stationary power input apparatus; and the power transmission members each is restricted to a single degree of freedom of motion from the stationary power input apparatus to the head.

In another feature of that aspect of the invention, the compressor piston is annular and has an axially extending passage formed there through to accommodate the other compression stage. In another feature, the power transmission has no slack between input of power to the power transmission at the stationary input apparatus and the head. In still another feature the power transmission members are connected to the head at moment connections. In a further feature the apparatus includes a controller operable to monitor motion of each of the transmission members and operable to co-ordinate motion of the transmission members relative to each other. In still a further feature each of the power transmission members is a shaft. The apparatus includes the stationary power input apparatus. The stationary power input apparatus includes drive cylinders and input power pistons. Each shaft of the power transmission members extends into a respective one of the drive cylinders and has a respective one of the input power pistons mounted thereto by which to drive reciprocation thereof. In yet still another feature, each of the power transmission members is a shaft held in a pair of first and second, axially spaced slide bearings that allow only longitudinal translation of the respective transmission members.

In another feature, each of the power transmission members is a shaft held in a pair of first and second, axially spaced apart slide bearings that allow only longitudinal translation of the respective transmission members. Each of the power transmission members is a shaft. The apparatus includes the stationary power input apparatus. The stationary power input apparatus includes drive cylinders and input power pistons. Each shaft of the power transmission members extends through a respective one of the drive cylinders and has a respective one of the input power pistons mounted thereto by which to drive reciprocation thereof between the pair of first and second axially spaced apart slide bearings. In a yet further feature, in cross-section transverse to the longitudinal direction the transmission members define vertices of a polygon. The piston has a centerline axis of reciprocation; and the centerline axis of reciprocation lies within the polygon. In yet a further feature the power transmission members include a first power transmission member and a second power transmission member, each of the first and second power transmission members has an axis of reciprocation, the piston has a centerline axis of reciprocation; and the axes of reciprocation of the first and second power transmission members are substantially diametrically opposed relative to the piston centerline axis of reciprocation. In still another further feature, both the power transmission members and the compressor piston are located longitudinally to one side of the head, the apparatus includes a spider, the spider defines mountings for the stationary power input apparatus and the spider has a central passageway defined therethough in which to mount the mating cylinder. In another aspect of the invention there is a two stage compressor feed apparatus operable to compress loose feedstock material, the feed apparatus comprising. There is a first compressor stage and a second compressor stage. The first compressor stage has a screw. The screw has a volute operable to drive the feedstock forward in an axial direction while compressing the feedstock. The second compressor stage has a compressor piston mounted to reciprocate in the axial direction, the second stage compressor piston has an axial accommodation permitting an end of the screw to extend therethrough. The second compressor stage has a stator and rams mounted to the stator in a rigidly fixed orientation parallel to the axial direction. The second compressor stage has a cylinder mounted to the stator. The cylinder is a mating cylinder for co-operation with the compressor piston. The second stage compressor piston has a first end and a second end. The second compressor stage includes a head. The second end of the compressor piston is mounted in a fixed orientation to the head. The first end of the compressor piston is distant from, and is oriented to face away from, the head. The rams include shafting extending to the head. The shafting constrains the head to a fixed orientation cross-wise to the axial direction. The rams are constrained to a single degree of freedom of motion in linear translation parallel to the axial direction between the stator and the head.

In another feature of that aspect of the invention the rams, the head and the piston are slacklessly connected. In still another feature, the rams include at least a first ram and a second ram, the first and second rams is mounted on substantially diametrically opposite sides of the second stage compressor piston. In yet another feature, the apparatus includes a controller and feedback sensors, the controller and feedback sensors being operable to co-ordinate motion of the first and second rams. In a still further feature the controller has a pre-set schedule of displacement as a function of time for the rams and is operable to cause motion of the rams to conform to the schedule. In yet another feature the first stage screw discharges to a chamber has a liquid extraction manifold and drain. In still another feature the first stage screw has a discharge tip, the discharge tip is surrounded by a sleeve. The sleeve is an axially stationary sleeve. The second stage piston surrounding the sleeve, and is axially reciprocable relative thereto. The sleeve has an interior face oriented toward the screw. The interior face of the sleeve has axially extending reliefs defined therein. In again another feature the feed apparatus discharges to a downstream conduit, the downstream conduit includes a cooling jacket, and the cooling jacket includes at least one internal helical wall. In still another feature the feed apparatus includes a drive mounted to turn the screw of the first stage compressor, the drive is a variable speed drive, and the controller is operable to adjust drive speed of the screw in co-ordination with motion of the second stage compression piston. In a further feature the two stage compression chamber gives onto a discharge, and the apparatus includes a discharge cone for seating athwart the discharge in opposition to passage of feedstock, the cone is axially reciprocable to permit egress of feedstock from the discharge, the controller is operable to adjust position of the discharge cone in co-ordination with motion of the second stage compressor piston. In yet another feature 15 the first stage compressor screw includes a volute has a continuously reducing pitch between successive turns of the volute. In a still further feature the cooling jacket has an inwardly facing wall defining a discharge passageway of the second stage compressor, and the inwardly facing wall tapers outwardly in the direction of flow.

In another aspect of the invention there is a process of compressing loose fibrous feedstock using a fibrous feedstock compression apparatus. The process includes passing the feedstock through a first stage of compression; employing a reciprocating piston to submit the feedstock to a second stage of compression in which that reciprocating piston is mounted to a head, and the head is mounted on actuating rams. The second stage of compression includes continuously sensing position of the rams during operation thereof. The process includes continuously co-ordinating motion of the rams.

In a feature of that aspect, the continuous coordination is achieved using real-time digital control of the rams. In another feature that control includes monitoring position displacement and motor current, and adjusting operation of the rams according to feedback from those sensors. In another feature the process includes operating the rams to a set schedule of displacement as a function of time. In a further feature, the process includes co-ordinating operation of the first stage of compression with operation of the rams. In still another feature the first stage of compression includes a screw compressor mounted to a variable speed drive, and the process includes continuous variation of the speed of the variable speed drive in co-ordination with operation of the rams. In yet another feature the apparatus includes an axially movable discharge cone, and the process includes actively adjusting one of (a) position; and (b) reactive force applied to the cone in co-ordination with motion of the second stage compressor piston.

These and other aspects and features of the invention may be understood with reference to the description and illustrations.

Brief Description of the Illustrations

The invention may be explained with the aid of the accompanying illustrations, in which: Figure Ia is a general arrangement in perspective of a high pressure process apparatus having a feed compressor assembly according to an aspect of the present invention;

Figure Ib is a profile or side view of the process apparatus of Figure Ia;

Figure Ic is a top view of the process apparatus of Figure Ia;

Figure Id is an end view of the process apparatus of Figure Ia;

Figure Ie is a longitudinal cross-section along the central vertical plane of the process apparatus of Figure Ia, indicated as section 'Ie - Ie' in Figure Ic;

Figure 2a is an enlarged perspective view of the feed compressor assembly of Figure Ia; taken from above, to one side and to one end;

Figure 2b is another view of the feed compressor assembly of Figure 2a from a viewpoint below and to one side thereof;

Figure 2c shows a vertical longitudinal cross-section of the assembly of Figure 2a taken on the longitudinal centerline thereof;

Figure 2d is a top view of the assembly of Figure2a with superstructure removed and an alternate motion transducer arrangement;

Figure 2e is an enlarged perspective detail of the screw drive of the first compressor stage of the compressor section assembly of Figure 2a;

Figure 3a shows a perspective view of the second compression stage of the compressor section assembly of Figure 2a;

Figure 3b shows a perspective sectional view of a portion of the compressor assembly of

Figure 2a from the first stage screw compressor sleeve to the end of a dewatering section;

Figure 3c shows a further partial perspective sectional view of the compressor assembly of Figure 2a from the end of the dewatering section to the end of the compression section output feed duct;

Figure 3d is a perspective view of a feed piston drive transmission assembly of the second compressor stage of the compressor section assembly of Figure 2a; Figure 3e shows a perspective view of the moving components of the second compression stage section of Figure 3a;

Figure 3f shows an opposite perspective view of the components of Figure 3e;

Figure 3g shows a perspective view of a frame member of the second compression stage of Figure 3a;

Figure 3h shows a sectioned perspective view of the compressor assembly of Figure 3a with the second stage compressor in a first or retracted or return, or start of stroke position; Figure 3i shows a view similar to Figure 3f with the second stage compressor in a second or advanced or end of stroke position;

Figure 4a shows perspective view of a feed cone assembly of the apparatus of Figure Ia, half-sectioned vertically along the centerline; and

Figure 4b shows an enlarged side view of the section of Figure 4a;

Figure 5 is a horizontal lateral cross-section of the apparatus of Figure Ia taken on section '5 - 5' of Figure Ic; and

Figure 6 is a side view in section on a vertical plane passing along the compressor section central plane of an alternate embodiment of compressor section to that of the apparatus of Figure Ia.

Detailed Description

The description that follows, and the embodiments described therein, are provided by way of illustration of an example, or examples, of particular embodiments of the principles of the present invention. These examples are provided for the purposes of explanation, and not of limitation, of those principles and of the invention. In the description, like parts are marked throughout the specification and the drawings with the same respective reference numerals.

The terminology used in this specification is thought to be consistent with the customary and ordinary meanings of those terms as they would be understood by a person of ordinary skill in the art in North America. Following from the decision of the Court of Appeal for the Federal Circuit in Phillips v. AWH Corp., and while not excluding interpretations based on other sources that are generally consistent with the customary and ordinary meanings of terms or with this specification, or both, on the basis of other references, the Applicant expressly excludes all interpretations that are inconsistent with this specification, and, in particular, expressly excludes any interpretation of the claims or the language used in this specification such as may be made in the USPTO, or in any other Patent Office, unless supported by this specification or in objective evidence of record in accordance with In re Lee, such as may demonstrate how the terms are used and understood by persons of ordinary skill in the art, or by way of expert evidence of a person or persons of experience in the art. In terms of general orientation and directional nomenclature, two types of frames of reference may be employed. First, inasmuch as this description refers to screws, screw conveyors or a screw compressors, it may be helpful to define an axial or x-direction, that direction being the direction of advance of work piece material along the screw when turning, there being also a radial direction and a circumferential direction. Second, in other circumstances it may be appropriate to consider a Cartesian frame of reference. In this document, unless stated otherwise, the x-direction is the direction of advance of the work piece or feedstock through the machine, and may typically be taken as the longitudinal centerline of the various feedstock flow conduits. The y-direction is taken as a horizontal axis perpendicular to the x-axis. The z-direction is generally the vertical axis. In general, and unless noted otherwise, the drawings may be taken as being generally in proportion and to scale.

Apparatus 20 - General Overview

A process apparatus 20 is shown in general arrangement in Figures Ia, Ib, Ic, Id and Ie. In the direction of flow of the feedstock material, there is a first assembly 22 that may be an input feeder or infeed conveyor at which feedstock material is introduced. For the purposes of this discussion, the feedstock may be taken as being corn stalks, or sugar cane stalks, cane bagasse or bamboo, or wood chips, or bark, or sawdust, and so on. The feedstock may be fibrous, may be anisotropic, and may by hydrophilic to a greater or lesser extent such as in the example of wood chips or wood flakes derived from the processing of green wood. The feedstock may have an initial moisture content of between 10% and about 65 % to 70% by weight, and may typically be processed with an initial moisture content in the range of 35 to 55 % by weight. Input feeder or input, or input conveyor 22 is attached to, and conveys feedstock material to, a multi-stage feedstock compression apparatus 24, which may be a co-axial feeder, that includes a first stage of compression indicated generally as 26, which may be a compression zone, such as a first stage compression zone or compression screw assembly, and a second stage of compression indicated generally as 28, which may be a second compression stage zone or piston zone assembly. Output from the piston zone, i.e., the second stage of compression 28, is fed through a discharge section to a reaction vessel in-feed assembly, indicated generally as 30. Assembly 30 includes a substantially vertically oriented digester drop chute or in-feed head chamber 32, an in-feed conduit or duct or insert, or digester insert 34; and a choke cone assembly 36. In- feed head chamber 32 is in essence part of the larger reactor, or reaction chamber or vessel 40, which may be referred to as a digester, and which includes not only head chamber or digester drop chute 32 but also a substantially horizontally, longitudinally oriented vessel, which may be termed the main reactor vessel or digester, 42. Main reactor vessel 42 may have an out feed or output assembly, which may also be called the discharge tube, 44. The entire apparatus may be mounted on a base or frame, indicated generally as 46. The reactor vessel may sometimes be termed a digester, and in other circumstances may be termed a hydrolyzer. In- feed assembly 30 is connected to main reactor vessel, or digester, 42 at a flanged coupling, indicated as 48. While only a single main reactor vessel is shown, other intermediate processing steps and their associate reactor vessels could also exist, and could be placed between in- feed assembly 30 and reactor vessel 42, connected at suitable flanged couplings such as coupling 48, as may be.

In one such process an organic feedstock in the nature of a loose lignocellulosic or partially lignocellulosic i.e., wood-based or wood-like feedstock is pressurized to perhaps 245 psig, and heated in the reaction chamber to saturated temperature of partially liquid water and partially water in vapour form. Moisture may be added or extracted, as may chemical solutions. The feedstock is held at this pressure and temperature for a period of time as it advances along the reaction chamber. At the discharge apparatus there is a more or less instantaneous, substantially adiabatic, and substantially isentropic expansion. The almost instant reduction in pressure may tend to result in the water trapped in the moisture absorbent wood chips or flakes tending to want to undergo a change of state from liquid to vapour almost instantaneously, with a resultant expansion within the feedstock that is perhaps not entirely unlike steam expansion in the making of popcorn. The result is that the fibres of the feedstock tend to be forced apart and in some sense beaten, making a finer, looser product. The product so obtained may have a relatively high ratio of surface area to volume, and may be "tenderized" in a sense, such that the fibres may more easily be broken down in digestive processes of microorganisms, e.g., bacteria, fungi, viruses, and so on, by which those fibres may be more readily converted to other chemicals, such as ethanol. Input Feeder or Infeed Conveyor 22

Input feeder or infeed conveyor 22 may include a collector vessel, which may be termed a reservoir, a trough, or an infeed screw hopper 50. It includes a feed advancement apparatus, or feeder, or infeed conveyor 52, which may be a conveyor, whether a belt conveyor or screw conveyor or auger 54 as shown. A drive, namely infeed conveyor drive 56 is provided to run auger 54, drive 56 being mounted on the far side of a down feed housing or drop chute 58, with the drive shaft extending in the horizontal longitudinal direction through the housing to auger 54. Drop chute 58 is mounted atop, and in flow communication with, an input housing, or feeder hopper, 60 of compressor apparatus, or co-axial feeder, 24.

First Stage Compressor or Compression Screw 26

Compression apparatus or co axial feeder 24 is mounted to a base plate 62, which is mounted to frame 46. First stage compressor or compression screw zone 26 includes a moving compression member, 64, a stationary compressed feedstock retaining member 66, input housing or feeder hopper 60, a bearing housing or bearing housing assembly 68 (and, inherently, the bearing contained therein), a drive identified as a compression screw reducer 70, and a drive coupling 72, and an array of preliminary infeed feed-stock conveyor members such as may be identified as triple screw assemblies 74.

Moving compression member 64 may be a compression screw 76. Compression screw 76 may include a volute having a variable pitch spacing between the individual flights or turns of the volute, either as a step function or, as in the embodiment illustrated, have a continuously decreasing pitch spacing as the tip of the screw is approached in the distal, forward longitudinal or x-direction. Compression screw 76 has a longitudinal centerline, and, in operation, rotation of screw 76 causes both forward advance of the feedstock material along the screw, and, in addition, causes compression of the feedstock in the longitudinal direction. The base or proximal end of screw 76 is mounted in a bearing, or compression screw bearing housing assembly 68 having a flange that is mounted to a rearwardly facing flange of input housing such as may be termed a feeder hopper 60. The keyed input shaft of screw 76 is driven by the similarly keyed output shaft of drive or reducer 70, torque being passed between the shafts by coupling 72.

Compression screw drive 70 includes a compression screw drive motor 80 mounted on its own motor base 78, which is mounted to base plate 62. Motor 80 may be a geared motor, and may include a reduction gearbox. Motor 80 may be a variable speed motor, and may include speed sensing, monitoring, and control apparatus operable continuously to vary output speed during operation. Feedstock entering drop chute 58 is urged by gravity into input housing 60, and generally toward compression screw 76. To aid in this migration, feed-stock conveyor members 74 may be used to direct the feed-stock to compression screw 76. Members 74 may have the form of two generally opposed, inclined banks of twin screws or triple screws or augers 82, mounted generally cross- wise to screw 76. Screws 82 are driven by motors 84 mounted to input housing 60. Screws 82, of which there may be four, six or eight, for example, may be in a V-arrangement.

Stationary compressed feedstock retaining member 66 may have the form of a compression screw sleeve 90 that is positioned about compression screw 76. In the embodiment illustrated compression screw sleeve 90 is both cylindrical and concentric with compression screw 76. Sleeve 90 has a radially extending flange at its upstream end, by which it is bolted to the downstream side face of input housing 60. Sleeve 90 may have an inner surface 92 that has a set of longitudinally extending grooves or channels defined therein, such as may be termed compression screw sleeve flutes 94. Flutes 94 may run parallel to the axial centerline of sleeve 90. As compression screw 76 operates, sleeve 90 provides radial containment of the feedstock as it is progressively compressed in the first stage of compression, and defines a portion of the flow passageway or conduit along which the feedstock is compelled to move. Sleeve 90 also has an outer surface, 96 that is cylindrical, and that interacts in a mating close sliding piston-and-cylinder-wall relationship with the second stage compressor. Outer surface 96 may be concentric with inner surface 92 and the axial centerline of sleeve 90 generally.

Second Stage Compressor or Piston Zone 28 The second stage of compression, or second stage compressor 28 includes a frame, or stator, or housing, or spider, indicated generally as 100; a moving compression member or piston 102; a feedstock retainer 104 that co-operates with moving compression member or piston 102; and a motive drive and transmission assembly 110, which may also be referred to as a ram drive assembly.

The frame, or housing or spider 100 (Figure 3g) is rigidly mounted to base plate 62, and hence to frame 46. It provides the datum or stationary point of reference for the second stage of compression, and links the major components of the second stage of compressions together. It has forward and rearward transverse frames, or wall members, or bulkheads, or plates indicated as 105, 106, and upper and lower longitudinally extending webs or walls, both left and right hand being indicated as members 107, 108. Walls 107, 108 terminate at flanges 109. Each of the transverse plates 105, 106 has a central eyelet, or relief, or aperture 101 formed there through to accommodate the duct or conduit, or cylinder in which feedstock is compressed and urged toward the reactor chamber. These eyelets are axially spaced apart, and concentric. This establishes the spatial relationship of that stationary conduit. Flanges 109 provide mounting points for the hydraulic rams and servo motors that drive and control compression member 102, thus establishing the fixed spatial relationship between the cylinder rods, the base, and the stationary conduit. Moving compression member 102 (Figure 3b) may be a reciprocating piston 112 having a first end 114, which may be a piston front face, and a second end 116, which may be a piston flange face. First end 114 is the downstream end that faces in the direction of compression and in the direction of motion of the feedstock and defines the output force transfer interface of second stage compressor 28 in general, and of moving compression member 102 in particular. First end 114 is an abutment end and is the head or face of the piston. First end or piston face 114 will be understood to include any wear plate or surface that may be formed thereon or attached thereto. A cylindrical piston wall or coating or skirt, or piston outside surface 118 extends rearwardly from first end 114 to second end 116.

Compressor piston 112 has a passageway 120 formed there through to permit feedstock from the first compressor stage to pass into the second compressor stage. Piston 112 has an inner surface 122 that permits reciprocation of piston 112 relative to screw 76 and sleeve 90. It is convenient that surface 122 be a round cylindrical surface that is concentric with outer surface 96 (the compression screw sleeve outside diameter), and the centerline axis of sleeve 90. First and second axially spaced apart seals, or rings 124 are mounted in seal ring grooves formed in skirt 118 near to second end 116. In operation rings 124, which may be the compression screw sleeve seals, provide a sliding seal between sleeve 90 and piston 112. Piston 112 also has an outer surface 126. It is convenient that outer surface 126, which may be the piston outside diameter, be a round cylindrical surface, and that this surface be concentric with the other surfaces 122, 96 and 92, although it need not necessarily be either round or concentric.

Feedstock retainer or dewatering split sleeve assembly 104 defines the outer cylinder wall 128 with which annular piston 122 co-operates, and to the extent that piston

112 is a moving member, cylinder wall 128 may be considered to be a stator, or stationary member. Retainer 104 may define a de-watering section or dewatering zone 130. De-watering section 130 performs both the function of retaining the feedstock as it is compressed and the function of a sieve or colander that allows liquids and air to be drained off. The term "de-watering" refers to squeezing liquid, or air, out of the feedstock during compression. While this liquid may be water, or predominantly water, it may be a juice or oil, or it may include removal of gases, such as air. The term "de- watering" is not intended to imply that the apparatus is limited only to use with water or water based liquids. Dewatering section 130 may include a dewatering zone housing 132, also known as a dewatering split sleeve assembly, a porous sleeve 134, also known as a dewatering sleeve insert, a flange member or seal cover 136 and piston seals 138. Housing 132 may have an upstream flange 140, a downstream flange 142 for rigid e.g., bolted, connection to spider 100, and a longitudinally extending wall 144 that runs between flanges 140 and 142. Wall 144 may have an array of perforations, or slots or drains spaced circumferentially thereabout to admit the passage of liquid squeezed out of the feedstock. Porous sleeve 134 slides axially into housing 132, and is retained in place by flange member 136. Flange member 136 is fixed to flange 140, e.g., by bolts. Porous sleeve 134 conforms to outer surface 126 of piston 112. Porous sleeve 134 may include an array of fine capillaries, or perforations or perforation channels that permit the generally radial egress of liquid liberated from the feedstock during compression. Flange 136 includes grooves for the axially spaced O-ring seals 138 that bear in sliding relationship against the outer surface 126 of piston 112. Base plate 62 has a drain located beneath dewatering section 130.

Motive drive and transmission assembly 110 (Figure 3d), which may also be termed a ram drive assembly, includes those members that produce the motion of piston 112 relative to the stationary base or point of reference, such as spider 100. They include a pair of first and second drive members, which may be identified as first and second actuator pistons 150, 152 that are each mounted between a pair of first and second axially spaced apart slide bearings 154, 156. Assembly 110 includes a plurality of transmission members, which may be identified in the illustrations as hydraulic cylinder rods, or simply "rods", identified as shafts 160, 162. If viewed in cross-section perpendicular to the line of action of piston 112 (also perpendicular to the respective lines of action of actuator pistons 150, 152), the array or arrangement or layout of the actuator pistons (in this instance two, 150, 152, but it could as easily be 3, 4, 5 or more), in which the line of action of compressor piston 112 (which is taken as lying at the centroid thereof along the centerline of the compressor section) is understood to be between, or intermediate, or nestled amidst, or lying in the center of the grouping of, the lines of action of the force input interface of the actuator pistons. In the case of actuator two pistons, (i.e., rather than three or more) while it is desirable that the lines of action of the actuator pistons and the line of action of the compressor piston be mutually co-planar, under some circumstances there may be a small degree of eccentricity where the line of action of the output piston, i.e., compressor piston 112 lies some distance out of the plane of centers of the input pistons. This eccentricity distance may be less than one half of the maximum outside radius ofpiston 112, and more desirably less than 1/10 ofthat radius length. The output piston may still be said to be generally amidst, or between, or intermediate the two input pistons when the centerlines of those pistons are eclipsed from one another by the diameter of the output piston. There may be any number of such pistons 150, 152 and shafts 160, 162. Where there are more than two such pistons and shafts they may be arranged such that if the assembly is sectioned transversely, and each shaft is taken as a vertex of a polygon, the centerline of the compression stages will fall within the polygon such that force transmission is not eccentric. It may be, for example, that the centerline axis of the first and second compressor stages lies at the centroid of any such polygon. Where there are three such pistons, for example, they may be arranged on 120 degree angular spacing about the centerline. Where there are more than two pistons, the terms amidst, intermediate or amidst may be used whenever the line of action, or centroid, of the output piston lies within the polygon whose vertices are defined by the lines of action of the input pistons. The actuator pistons need not be precisely equally angularly spaced about the output piston, but may be spaced in a generally balanced arrangement.

Shafts 160, 162 may either be mounted to the rams of a respective piston, or, as illustrated, may pass directly through a piston, be it 150 or 152, and may have the piston head members against which the pressurized working fluid acts mounted thereto within the piston cylinder, 164, 166. In the usual manner, admission of fluid into one side of cylinder 164 (or 166) will drive shaft 160 (or 162) piston to the retracted or return position shown in Figure 3g, while admission of fluid to the other end of cylinder 164 (or 166) will cause shaft 160 (or 162) to move in the other direction to compress the feedstock. Drive assembly 110 may have servo valves 170, 172 for this purpose. Pistons 150, 152 may be either pneumatic or hydraulic. In the embodiment illustrated, pistons 150, 152 may be understood to be hydraulic.

Assembly 110 may also include position or motion transducers, indicated as 174, 176 mounted either directly to shafts 160, 162 or to slave shaft members such as may permit the instantaneous position of shafts 160, 162 to be known, and their change in position per unit time, i.e., velocity, to be calculated. Shafts 160, 162 terminate, and are attached to, a cross-member, or frame, or yoke, a ram or ram plate, a cross-head or simply a head 180 (Figure 3e). The connections of shafts 160, 162 may be slackless connections, and may be moment connections. That is the connections may be rigid such that there is no degree of freedom of motion between the end of shafts 160 and 162 with respect to either longitudinal displacement along the x axis or angular rotation about the y or z axes. The connections may be splined, may include a shoulder, and may be bolted. Head or piston ram 180 may have the form of a yoke or plate having a central opening to accommodate reciprocation of objects relative thereto through the central opening, such as the elements of the first compressor stage, notably sleeve 90 and screw 76. In this instance head 180 has an internal annular flange or shoulder to which second end 116 of piston 112 is bolted. It may be that pistons 150, 152 have their own integral rams or shafts, to which shafts such as shafts 160, 162 may be mounted axially as extensions. Whether this is so, or whether shafts 160, 162 are monolithic members or members that are assembled from two or more sub-components, the use of axially spaced apart slide bearings constrains shafts 160, 162 to a single degree of freedom of motion, namely translation along the motion path defined by slide bearings 154, 156. That motion path may be straight line axial displacement.

In contrast to some earlier machines, apparatus 20 may be free of such things as a large flywheel, a rotating crankshaft, long and heavy connecting rod assemblies, and so on. Since it may be desirable to avoid unduly large live loads as piston 112 reciprocates, it may be that there are only two such shafts and pistons. In this example, the entire live load is made up of piston 112, head 180, in essence a flanged ring with lugs, and shafts 160, 162. Moreover, the placement of pistons 150, 152 to the same side of head 180 as piston 112 may tend to make for a relatively compact assembly in the longitudinal direction, that length being less than the combined length of sleeve 90 and de-watering section 130. The length of the transmission drive train so defined may be expressed as a ratio of the output inside diameter of de-watering section 130 or tailpipe, or hydrolyzer inlet insert 196, that ratio lying in the range of less than 8:1, and in one embodiment is about 5:1. Another potential measure of live load is the lateral compactness of the unit., as measured by the center spacing of the rods. In one embodiment the stroke of piston 112, signified as may be about 3 inches, the bore may be about 4 inches, and the lateral spacing of the rods may be about 1 1 inches. The cantilever distance or overhang of the transmission is defined as the maximum length (i.e., in the retracted position) of the rods, shafts 160, 162 plus the ram plate, head 180, that extend beyond the nearest bearing. In one embodiment this may be about 10". Taking these values in proportion, in one embodiment the ratio of stroke to bore may be less than square (i.e., stroke/bore < 1), and in some embodiments less than 4:5. The ratio of overhang to piston stroke may be in the range of 2.5: 1 to 3.0:1. The ratio of overhang to lateral center to center distance of rods 160, 162 may be in the range of less than 1 and may be 15/16 or less. In one embodiment it may be about 5/8.

A ram driven by hydraulic cylinders was used in US Patent 4, 119,025. However, as seen at Figure 2 of that patent, quite aside from lack of feedback and positive control, there are at least two other points at which additional degrees of freedom of motion are introduced between the rigid frame of reference defined by the main conduit, and the output at the piston, those degrees of freedom being introduced by the pivot connection of the rams to the frame, and by the pivot and clevis pin arrangement between the rams and the slides. At each of these points slack, or tolerance build-up, can be introduced into the system. In the embodiment of apparatus 20 illustrated herein, the drive transmission is slackless from the point of application of input force by the pressurized working fluid at pistons 150, 152 to the interface between head 180 and second end 116 of piston 112, and, indeed to first end 114 of piston 112 at which output force is applied to, and work is done on, the feedstock. There are no intermediate points at which extraneous degrees of freedom are introduced into the system. Further, inasmuch as it may be desirable to maintain the angular orientation of piston 112 relative to the centerline, it may also be desirable not to give rise to unnecessary or unnecessarily large eccentric or unbalanced loads. To that end, it may be that the centerline of piston 112 is either substantially co-planar therewith or lies fairly close to a plane defined by the axes of shafts 160, 162. "Fairly close to" in this context may be understood as being less than 1/10 of the outside diameter of piston 112, or less than one diameter of shaft 160, 162 away from being co-planar. Expressed alternatively in terms of angular arc, those pistons may lie in the range of 150 degrees to 210 degrees angular spacing, and may be about 180 degrees apart.

Drive assembly 110, or, more generally apparatus 20, may include a controller, indicated generically as 182 operable continually to monitor output from transducers 174, 176 and continually to adjust servo valves 170, 172 to control the position and rate of motion, be it advance or return, of piston 112. The clock rate of the controller microprocessor may be of the order of perhaps 1 GHz. The frequency of reciprocation of piston 112 may be of the order of 50 to perhaps as much as approaching 200 strokes per minute. A more normal cautious range might be from about 75 - 80 strokes per minute (1 ¹ A to 1-1/3 Hz) to about 150 strokes/min (2 ¹ A Hz), with a typical desirable speed of perhaps 100 strokes per minute (1 ¹ A to 1 ³ A Hz). Thus, the motion of piston 112 is many orders of magnitude slower than the ability of the sensors and processor to monitor and modify or modulate that motion. Controller 182 may be pre-programmed to include a reference or datum schedule of displacement as a function of time to which piston 112 is to conform. That schedule may establish a regime of relatively smooth acceleration and deceleration. The schedule may also be asynchronous, or temporally asymmetric. That is, the portion of the cycle occupied by driving piston 112 forward against the feedstock may differ from the unloaded return stroke. For example, the compression stroke may be longer, and the motion of piston 112 slower, than the unloaded return stroke. In one embodiment a ratio of this asymmetry of compression to retraction may be in the range of about 4/5: 1/5 to 5/8:3/8, such that the majority of time is spent compressing and advancing the feedstock. This proportion may be deliberately selected, and may be subject to real-time electronic control, in contrast to previous apparatus.

The inventor has observed that power consumption (and, indeed, the tendency to gall or otherwise ruin the sliding surfaces) may be reduced if piston 112 can be discouraged from deviating from its orientation and from contacting the sidewall, and particularly so if a thin layer of liquid can be established between piston 112 and the adjacent cylinder wall; or if such deviation should occur, if it can be sensed before it grows unduly large and adjustments or corrections be made accordingly to tend to minimize and correct the deviation. The deviations in question may be of the order of a few thousandths of an inch, such that even small amounts of slack or tolerance build up may have a noticeable deleterious effect. To that end, controller 182 may also be programmed to monitor each shaft and actively to adjust servo valves 170, 172 to cause the various shafts to move in a co-ordinated manner in which the orientation of piston 112 relative to the direction of advance along the centerline is maintained substantially constant. With a high digital clock rate in the controller's microprocessor, to which in contrast the speed of the cylinder rod motion is infinitesimally slow, the degree of accuracy that can be obtained may be quite high. Further, to the extent that the junction of shafts 160, 162 (however many there may be) may define a moment connection permitting substantially no angular degree of freedom of head 180 or piston 112 about the y-axis (i.e., the horizontal cross-wise axis), and shafts 160, 162 are held in spaced apart slide bearings 154, 156, that may bracket pistons 150, 152, a high level of control is established over the angular orientation of the drive transmission assembly about both the z and y-axes.

Downstream of de- watering section 130 there is a tail pipe or discharge section, which may also be identified as a compression tube 184 through which compressed feedstock is driven by the action of the compressor stage (Figure 3c). Discharge section compression tube 184 may include a cooling manifold, or compression tube cooling jacket, 186 having an inner wall 187, an outer wall 188 spaced radially away from inner wall 187, and an internal radially outwardly standing wall or web 189. Web 189 may be in the form of an helix, and as such may tend to compel cooling fluid, which may be water or glycol based, to circulate about the jacket in a generally helical circumferential path from coolant inlet 190 to coolant outlet 191. Inner wall 187 may have a divergent taper in the direction of flow. The angle of that divergent taper may be of the order of 30 minutes of arc. Discharge section tube 184 ends at a downstream flange 192. Flange 192 mates with a corresponding flange 194 of the reactor vessel in-feed tail pipe, or digester insert 196, which may typically be of slightly larger inside diameter than the downstream end of discharge, but which may also have the slight outward flare or taper of section tube 184. Both inside wall 187 and outside wall 188 may be circular in cross- section, outside wall 188 being cylindrical and inside wall 187 being frusto-conical. The combined length, from the dewatering section downstream flange to the choke cone seat, express in term of a length to diameter ratio, taking diameter at the outlet flange of the dewatering section, may be in the range of more than 5:1 and up to about 8: 1 or about 10:1. In one embodiment this range may be about 6.4: 1.

The compression process may tend to heat the feedstock. It may not be desirable to overheat the feedstock, and a location of maximum heating may be in the high friction shear zone immediately adjacent to inside wall and immediately in front of first end face

114 of piston 112. To the extent that the feedstock is a biological material containing natural sugars, once the sugars of the feedstock start to brown, for example, the quality of the feedstock and the completeness of the subsequent activity in the reaction chamber may be impaired. The cooling of inside wall 187 may tend to discourage or deter this heating process. In addition, the retention of a modest moisture layer in liquid form about the outside of the feedstock slug may tend to provide lubrication between the discharge wall and the feedstock. The inventors have observed that this effect, and, conversely, the absence of this effect, may noticeably effect the power consumption of the apparatus. It appears to the inventors that this effect may be enhanced by one or another of close control of piston position, close control of, and enhancement of the evenness of, cooling, and close control of pressure variation during compression. In the inventors view, operational temperatures of the fibre at the wall may be kept below 65 C for wood based fibers, and preferably about 60 C. The wall surface of wall 187 may be maintained in the range of about 35 to 40 C, with a maximum of 65 C. Choke Cone Assembly 36

Choke cone assembly 36 (Figures 4a and 4b) is mounted to vertical pipe or hydrolyzer drop chute 200 in axial alignment with, i.e., concentric with, the horizontal discharge pipe of the compression section, namely digester insert 196. It includes a horizontal stub pipe, or choke cone nozzle 202 in which a longitudinally reciprocating shaft, or choke cone shaft 204 is mounted. The inner end of shaft 204 carries a pointed, generally conical cap or choke cone 206 that is mounted in concentric axial alignment with digester insert 196. Choke cone 206 has a broadening skirt 208 such as may seat in the end of insert 196 at full extension. Assembly 36 also includes a reciprocating drive 210 mounted in axial alignment with shaft 204 on the centerline of the unit, and a sensing assembly 212, which may be a load cell, by which to sense the position of shaft 204, and hence choke cone 206, and the force acting against choke cone 206. Shaft 204 is mounted on a pair of axially spaced apart bearings 205, and passes through a set of seals or glands, identified as choke cone packing rings 216.

In operation, if there is no load on assembly 36, such as may occur when there is no feedstock material in tail pipe 196, shaft 204 moves forward to full travel to seat in the end of tail pipe 196. As feed stock collects in tail pipe 196 it is initially not significantly compressed, and tail pipe 196 remains in place as the wad of feedstock builds against it. Eventually the wad becomes substantially continuous, and is quite tightly packed, sufficiently so to lift, i.e., displace the cone 206, from its seat, and to permit egress of feedstock from tailpipe 196. Cone 206 then serves two functions, namely to maintain pressure on the end of the wad or pad of feedstock, and to split up that wad or pad when it leaves insert 196 and enters the reactor chamber. Both compression tube 184 and digester insert 196 may have the gentle longitudinal flare or taper noted above. In operation, when piston 112 retracts, pressure from choke cone 206 tends to push longitudinally rearward on the plug of feedstock in insert 196 and tube 184. Since these members are tapered, this pressure tends to wedge the plug in place, the plug tending not to more rearwardly because of the taper. This situation remains until piston 112 again moves forward, overcoming the force applied by choke cone 206 and "lifting" the plug of feedstock off the tapered walls against which it is wedged, and urging the plug along in the forward direction. Through this process the sensors and control circuitry may be employed to determine the force to apply to shaft 204 to maintain stabilising pressure against the plug, and the timing to retract choke cone 206 as piston 112 advances, thereby tending to smooth the process.

Main Reactor Vessel or Digester Assembly 40

The main reactor chamber, or digester assembly may include a pressure vessel 220, which may have the form of a substantially cylindrical tube, with suitable pressure retaining end fittings. The cylindrical tube may be inclined on a gentle downward angle from input to output. Pressure vessel 220 may have a feedstock conveyor, or which one type may be a central retention screw 222 driven by a main motor and reduction gearbox 224. Retention screw 222 may include a hollow central shaft that is connected to a source of heat, such as steam heat, and to the extent that it is heating the volute, or paddles, or retention screw flights 223, those flights are also radially extending heat exchanger fins that establish a heat transfer interface. One advantage of such an arrangement is that it permits the introduction of heat into the reactor vessel, and hence into the feedstock, without changing the moisture content in the feedstock. Screw conveyor 222 may fit generally closely within the inner wall of the reactor vessel, such that as the screw turns, the feedstock may tend to be driven or advanced along the central axis. Pressure vessel 220 may be a double walled pressure vessel, and the space between the inner and outer walls may be connected to a source of heat, such as steam heat, it is heating the volume of the vessel as well, or may be insulated and may house heating elements, as may be appropriate for the particular industrial process for which apparatus 20 is employed. Pressure vessel 220 may be provided with a number of taps or nozzles or spray nozzles 214, 218 at which liquids or chemicals in fluid or solid form may be introduced or extracted according to the nature of the process. Pressure vessel 220 may also include heating apparatus, again, according to the desired process. As noted, feedstock is directed into the main body of the pressure vessel by the vertical digester drop zone. Feedstock may leave pressure vessel 220 at the output assembly 44. The pressure in the reactor vessel, or digester, may, in the broadest range, be in the range of 75 - 500 psig. A narrow range of 170 to 265 psig may be employed, and a still narrower range of 190 to 235 psig may be desired if the process is a steam only process. If acids are used to aid in breaking down the wood fibres, the pressures may tend to be toward the lower ends of these ranges. Temperatures in the reactor vessel may typically be in the range of 170 - 220 C, and, more narrowly, 200 - 210 C. The residence time of feedstock in the reactor chamber may be of the order of 4 to 14 minutes and typically 5 to 9 minutes. Output or Discharge Screw and Discharge Tube Assembly 44

The discharge, de-compression, or output assembly, which may also be termed the discharge screw and discharge tube assembly, 44 may be mounted cross-wise to the main longitudinal axis of the reactor vessel, e.g., pressure vessel 220. There may be two pipe stubs, those being a drive stub and an output stub or pipe flanges 226, 228 respectively mounted to, and forming arms or extensions of, pressure vessel 220. A screw or auger or discharge screw 230 may be mounted between the retention screw bearing arrangement and digester discharge tubes 226, 228, e.g., at a level rather lower than the centerline of pressure vessel 220. Auger 230 may be driven by a motor, or discharge screw drive 232. Screw 230 passes beneath, and clear of, the main screw, namely pressure vessel retention screw 222. The volute of retention screw 222 ends just before, i.e., longitudinally shy or short in the direction of advance of, cross- wise mounted discharge screw 230, as shown in Figure Ie. The transverse discharge screw 230 feeds an output duct, or pipe identified as discharge tube 234, which, in turn carries feedstock to an outflow governor, such as an outlet valve 240, which may be termed a blow valve. The output duct or pipe or discharge tube 234 in effect defines a first-in-first-out output collector or accumulator or discharge antechamber. It is conceptually somewhat similar to an electrical capacitor in which a charge or plug of material for output can be accumulated in the collector awaiting discharge. The plug has in part a function somewhat akin to a wadding in a gun barrel where, in desired operation, there will always be a pad or plug or wadding of porous feedstock obstructing the outflow. The size of the pad or plug waxes and wanes as the outflow valve opens and closes extracting material from the downstream end of the pad or plug, with the pad being constantly replenished on its upstream end by the action of screw 230. Transverse screw 230 then functions as a drive or packer. It forms and packs a wad or charge or pad of feedstock in the collector. If the pad is sufficiently large, the quantity of the charge will be less than the amount discharged in one cycle of the valve. The end of stub 228 extending longitudinally beyond the tip of auger 230 may have a flare, or outward taper in the downstream direction, comparable to the flare of the infeed pipe from the compressor discharge section, to discourage the feedstock from jamming in the pipe. The taper may be about 30 minutes of arc.

Outlet valve 240 may be a ball control valve 242, of which one type is a Neles Series E ceramic ball valve such as may be used in abrasive applications where erosion resistance may be desirable and which may not necessarily be shown to scale in the illustrations. The flow path of this valve may be lined with a material that includes magnesia partially stabilized with zirconia. Valve 242 is a motorized valve, and may include a drive or drive motor, identified as blow valve servo motor 244, which may be a stepper motor with continuous speed variation. Valve 242 may include an internal ball with continuous 360 degree rotation. It may be appreciated, each time the ball turns 180 degrees, an incremental discharge or "blow" will occur in view of the pressure drop from Phigh inside pressure vessel 220 to P _am bient outside pressure vessel 220. Valve 242 may be a uni-directional valve, or may be used only to turn uni-directionally, be it always clockwise or always counter-clockwise, rather than reversing between the two. Valve 242 is an electronically controlled valve in which the operation of motor 244, and the speed variation thereof, may be made in response to both pre-programmed values and parameter values sensed in apparatus 20 more generally. Those parameters may include pressure immediately upstream of valve 242, drop in that value, rise in that value, differentials thereform of rate of change thereof; may include temperature, moisture of other values in the process, and may include parameters related to motor load and performance from which the presence of feedstock in the accumulator may be inferred, or a fault inferred, an easily monitored value being electric motor current draw. As above, the clock speed of the digital electronic monitoring and control equipment may be of the order of IGHz, while the frequency of blows may be of the order of 30 - 60 Hz. A typical internal pressure may be in the range of 245 psig at a saturated mixture of steam, for example. The rate of motion of ball valve 242 may be such that the period of opening is somewhat like the opening of a camera shutter or aperture, or nozzle, and in that short space of time the feedstock exits the reactor in what is more or less an explosion. To the extent that there is a level of moisture in the reactor and absorbed in the feedstock, it may tend to be a steam explosion. The length of the outlet duct past the end of the auger may be in the range of 4: 1 to 10: 1 times its diameter. All of the motors of apparatus 20 may be servo motors with continuously variable, digitally controlled speed. The pressure immediately upstream of ball valve 242 may be monitored, as may motor current on the discharge screw drive, namely motor 232. When there is a "no load" current in motor 232, the controller may signal an increase in speed of motor 232 to attempt more quickly to re-establish an adequate plug of feedstock in the outflow collector. Conversely, where the load current is too high, as may indicate a blockage, the controller may signal a decrease in motor speed until current returns to an acceptable level with the discharge of material when valve 242 is opened, or, if this is not does not resolve the matter within a set period, t _Lo n _g , e.g., 1 sec or 2 sec, and the controller times out, the controller may then signal cessation of motor current to motor 244 to move to a more open discharge period. As may be appreciated, rapidly depressurizing feedstock may be blown through the open aperture or nozzle defined by ball valve 242 at quite high velocity, particularly if, at the same time, there is an adiabatic, isentropic expansion as the moisture in the feedstock changes state from liquid to gas, e.g., water vapour. Processed feedstock leaving ball valve 242 may be discharged through outlet ducting, which may be in the form of a broadening passageway, which may be a diffuser, indicated conceptually as 246. The output flow may then expand and decelerate in the diffuser. The outlet ducting may be connected to a settling chamber or cyclone, indicated conceptually as 248, at which the processed feedstock may be separated from the liberated steam, and may further decelerate and settle out of the carrier gas (i.e., steam) flow, and may be collected, and whence it may be removed to storage or for further processing, such as use as feedstock in producing ethanol or other products. Motor 244, diffuser 246, and cyclone 248 may not be shown to scale in the illustrations. The explosion of feedstock at the outlet may tend to be most effective when the pressure differential is greatest, the reduction in pressure most rapid. Valve 242 then acts like a relatively rapidly moving shutter. It may be advantageous for the shutter to be open only for a very brief moment so that a reduction in driving pressure at the ball valve is negligible. To that end, variable control of the ball valve servo motor may permit both the time of exposure of the shutter, i.e., the time period at which the valve is open, and the interval between openings of the shutter to be controlled continuously as a function of time. It may be desirable for the opening time period, to _pe n, to be as short as practicable, many short bursts being thought to be more effective in treating the feedstock than a smaller number of longer bursts or blows. Typically, the ratio of valve closed time, tciosed, to valve open time, to _P en, may be of the order of perhaps 3:1 to 10:1. The total time, tτ _o tai, for 180 degrees of rotation of the valve may be as little as ¹ A second, including both open and closed time, or 120 Hz, corresponding to a mean rotational speed of roughly 60 r.p.m. at two openings per revolution. A more typical total time for 180 degrees of rotation might be 1 s to 2 s, or 60 - 30 Hz. In normal operation the valve would be expected to move or cycle between open and obstructed or closed positions 40 times a minute or more. The valve may be open for Is, closed for 5s or closed for 8 s. Alternatively, the valve may be closed for 1 s, and open for 1/5 or 1/8 second. In operation, the auger motor may have a full load current draw, I _f1 , , somewhat in excess of 10 Amps, and a no load current draw of 3 Amps. When the current draw exceeds 80 % of full load it may be inferred that there is a plug of feedstock in the outlet pipe, and the control may signal for the valve to be opened. The valve may have a target open time period, t _Ref , perhaps of % s. possibly somewhat less such as 1/5 s to or 1/8 s. If the pressure immediately upstream of the valve falls 2 psig prior to the expiry of that time period, e.g. ¹ Zi s, the control may signal for the valve to close. Motor current may drop to a value close to "no load", perhaps 40% or less of the full load value. If, abnormally, that pressure drop should exceed a reference value, Pϋr _o pR _e f, be it as much as 4 or 5 psig., the programmed logic of controller may infer that there is no plug left in the outlet pipe accumulator, which is undesirable. Valve 242 must then be closed immediately. When valve 242 is closed, discharge screw 230 replenishes the plug with feedstock until the threshold motor current draw is reached. Alternatively, if the valve is open for the target time period, tR _e) , ¹ A s, perhaps, and the motor current does not fall below some threshold value, such as 50 % of full load, then the closed portion of the cycle needs to be shorter. If the closed portion becomes as short as possible, (though not necessarily so, assumed to be tR _e f,) due to the practical physical limitations of the valve, or a limit on the value imposed by the controller as a speed governor, then the length of opening time must be increased. If there is a high current draw at the same time as a low pressure signal, a fault signal will be generated and a warning or alarm signal sent to the operator and the process taken off-line. Then, in summary, the foregoing describes an apparatus and method for processing fibrous organic feedstock. The apparatus includes a compressor operable to raise the fibrous organic feedstock to a processing pressure; a reactor vessel through which to process the fibrous organic feedstock under pressure; and a discharge assembly mounted to receive the fibrous organic feedstock of the reactor vessel. The discharge assembly includes a collector and a drive member operable to pack the fibrous organic feedstock into the collector. An outflow governor is mounted to the collector. The outflow governor is movable between a closed position for retaining feedstock in the collector and an open position for permitting egress of the feedstock from the collector. The outflow governor has an outflow governor drive. The outflow governor drive has a continuously variable speed control. The speed control is operable to alter both the duration of the outflow governor in the open position and the ratio of time spent in the open and closed positions. The variable speed control is operable to cycle the outflow governor between open and closed conditions in excess of 40 times per minute. The apparatus includes sensors operable to monitor pressure upstream of the outflow governor and the digital electronic controller is connected to cause operation of the outflow governor in response to pressure signals and in response to load sensed in the collector, by the proxy of monitoring motor current. The apparatus includes at least one heat transfer interface at which heat may be added to said reactor vessel and any contents thereof, and at least one moisture modification input or interface by which to modulate moisture level within said reactor vessel, whether by extraction at de-watering section 130 or taps 218, or by introduction at taps 214 (or 218, as may be). The outflow governor is connected to open in response to presence out feedstock in the collector and sensing of a minimum outflow pressure threshold.

The apparatus may include control logic to (a) shorten outflow governor closed time when resistance to packing of the outfeed collector increases; (b) lengthen outflow governor open time when resistance to packing of the outfeed collector increases; (c) increase the ratio of outflow governor open time to outflow governor closed time as proportions of total outflow governor cycle time; (d) bias said outflow governor to reduce outflow open time to a minimum threshold value; or (e) immediately to move said outflow governor to the closed position when pressure upstream therefrom falls below a designated set point value, or all of them. The process for treating a loose fibrous feedstock includes establishing the loose fibrous feedstock in a reactor vessel at an elevated pressure relative to ambient; passing charges of the feedstock through a sudden expansion, which may be substantially adiabatic and isentropic; and controlling decompression cycle parameters in real time with a variable speed outflow valve.

The process may include using ball valve 242 as the variable speed outflow valve, and it may include driving ball valve 242 uni-directionally and varying speed in that one direction. The process includes employing sensors to observe pressure in the reactor vessel upstream of the outflow valve, and modulating operation of the outflow valve in response to pressure sensed upstream of the outflow valve. It may include at least one of: (a) maintaining the outflow valve in an open condition for less than one second; (b) maintaining the outflow valve in an open condition for to _Pe n, and maintaining the outflow valve in a closed condition for tciosed where to _P en is less than ¹ A of tciosed; (c) sensing pressure drop upstream of the outflow valve while the outflow valve is open, and driving the outflow valve closed immediately if pressure drop exceeds a set threshold value, Puropr _e f; (d) sensing presence of feedstock in a collector mounted upstream of the outflow valve, and inhibiting opening of the outflow valve unless feedstock is inferred to be present; (e) setting a minimum open condition time reference value, t _Ref , for the outflow valve, and biasing the opening time of the outflow valve, to _pen , toward tR _ef ; (f) opening and closing the outflow valve in the range of 20 to 120 times per minute.

The process may include (a) opening and closing the outflow valve at least 40 times per minute; (b) maintaining a total cycle time, ttot _a i, of less that 2 seconds, where ttotai is the sum of valve open time, to _P en, and valve closed time, tci _os ed; (c) maintaining a ratio of valve open time, to _pen , and valve closed time, tciosed that is less than 1 :5, or all of them. It may include providing a feedstock collector upstream of the outflow valve; providing a drive to pack feedstock into the collector; monitoring drive motor electrical current; monitoring pressure immediately upstream of the outflow valve; inhibiting opening of the outflow valve until drive motor electrical current exceeds a threshold current value, I _va iveopen, and reactor pressure immediately upstream of the outflow valve is at least as great as a pressure minimum discharge triggering value, P _va i _ve open; closing the valve at the earliest of: (a) timing out against a set reference value, t _Long ; (b) sensing a drop in electrical motor current to below a set reference value l _Lowref ; (c) sensing a drop in pressure greater than a set reference value Pu _ropref . The process may include biasing the outflow valve open time period, to _pe n to the shortest period of time consistent with the foregoing operating conditions, and biasing the ratio of outflow valve open time, to _pen , to outflow valve closed time, tciosed, to the minimum value consistent with the other operating conditions. The process may include heating the feedstock in the reaction chamber to a temperature corresponding to saturated water vapour temperature at the pressure of the reactor chamber, or maintaining a moisture level within the reaction chamber in a preset range, or both. It may include a ratio of valve open time, to _P en, to valve closed time, tci _osed , falls in the range of 3:1 and 10:1, or more narrowly, a ratio of valve open time, to _pen , to valve closed time, tci _osed , falls in the range of 5:1 and 8:1. Outflow control valve 242 may be inhibited from opening when the current draw is less than 70% of In, and may be inhibited from closing when In is greater than 50 % of In. The process may have a target control valve time open, t _Open , of less than ¹ A second. The reactor vessel may be maintained at a pressure in excess of 190 psig, and temperature in the reactor vessel is maintained at the corresponding steam table saturated temperature. More narrowly the target reactor vessel pressure is 245 psig +/- 5 psig. Control valve closing may be initiated on a fall in pressure of 2 psig, and is immediate on a fall in pressure of 5 psig.

Alternate Second Stage Compressor

Figure 6 shows a sectioned view of an alternate second stage compressor or piston zone arrangement to that of second stage compressor 28 described above.

As described above second stage compressor 28 provides an apparatus that has only a single degree of freedom of motion (i.e., linear reciprocation in the x-direction) and no slack between the force input interface at pistons 150, 152 of the hydraulic cylinders and the force output interface where the piston front face of first end 114 of piston 112 meets with the feedstock work piece material being compressed. To the extent shafts 160, 162, crosshead 180, and piston 112 may be considered a single rigid body, all points of that rigid body being movable relative to a reference datum, such as the stationary cylinder end wall of one of the actuator pistons, be it 150 or 152, as may be.

In the example of motion drive and transmission assembly 110, the mechanical drive train, or transmission, or rods 160, 162, and head 180, is connected to piston 112 at an input force transfer interface or connection at the mounting at second end 116. However, subject to maintaining a suitable range of longitudinal travel, it could have been connected at some other input force interface connection location elsewhere along the body of piston 112 between first and second ends 114, 116. As shown in Figure 6, in an alternate arrangement the input piston arrangement may be that of a single piston, and it may be that of an annular piston, or peripheral piston (or array of peripheral pistons) where the body of the piston extends outwardly from the piston wall itself. For example, an alternate motion drive and transmission assembly is indicated generally as 250. It includes a moving compression member identified as an output or compression piston 252, which is the "second stage compressor" operable to provide the second stage of compression relative to the first stage of compression associated with compression screw 76 (which remains as before). Like piston 112, compression piston 252 is hollow and extends peripherally, (or circumferentially) about an internal sleeve such that compression piston 252 is shaped to extend about at least a portion of the first compression stage. In the embodiment shown this internal sleeve is compression screw sleeve 90, as before. There are piston rings and seals between sleeve 90 and piston 252 in the same manner as between sleeve 90 and piston 112 described above. Sleeve 90 is stationary, being rigidly mounted to feeder hopper input housing 60, as previously.

Piston 252 includes a cylindrical body with a bore defined therein just like the bore of passageway 120. The cylindrical body includes a first end 254 and a second end 256. Like first end 114, first end 254 defines the output force transfer interface at which output piston 252 works against the feedstock materials to be compressed. Second end 256 has the form of a trailing skirt. The bore may be such that the body may be conveniently a hollow round circular cylinder, though it need not necessarily be circular, having an inner surface, just like surface 122, facing sleeve 90, and an outer surface 258 facing away from sleeve 90. The inner surface may have appropriate grooves for rings or seals for co-operation with sleeve 90, as may be. As with first end 114, first end 254 reciprocates in the longitudinal direction (i.e., parallel to the x-axis) within the cooperating mating cylinder of the input end of dewatering section 130, with which its shape conforms, and has the same relationship of seals and rings. Dewatering section 130 is rigidly mounted to discharge section tube 184, just as before. Output piston 252 is, in effect, carried within the body of an input actuator 260, which may be identified as an hydraulic cylinder 262. Expressed differently, the cylindrical body of piston 252 passes through input actuator 260, such that input actuator 260 may be said to be mounted peripherally about part of the length of piston 252. In this instance, hydraulic cylinder 262 has a body 264 that is rigidly mounted (e.g., bolted or welded) to base plate 62, and, ultimately, to frame 46. Body 264 includes a central portion, or core, 266, a first end plate 268, and a second end plate 270. Core 266 has a bore 272 formed therein, bore 266 being sized to accommodate the outwardly extending flange or wall or shoulder, identified as portion 274 that protrudes radially outward from the predominantly cylindrical body of piston 252., and extends peripherally thereabout. Wall portion 274 includes a circumferentially extending peripheral wall or surface 276 that includes suitable grooves for seals 278 that slidingly engage the inwardly facing actuator cylinder wall surface 280. Portion 274 includes a first shoulder face, which may be a first annular surface 282, and a second shoulder face, which may be a second annular surface 284. Surface 282 faces toward first end plate 268, while surface 284 faces toward, and stands in opposition to, second end plate 270.

First end plate 268 has a bore formed therein of a size closely to accommodate a first end portion 286 of outer surface 258 in a sliding relationship, an appropriate groove, or seat, being provided for an O-ring or other seal as indicated. Similarly, second end plate 270 has a bore formed therein to accommodate a second end portion 288 of outer surface 258, again with a groove and a seal. In this way two annular chambers are formed, those chambers being a first, or retraction or return, chamber 290 bounded axially between first end plate 268 and first annular surface 282, and bounded radially and circumferentially by portion 286 and surface 280; and a second, or advance, chamber 292 bounded axially by second end plate 270 and second annular surface 284, and bounded radially and circumferentially by second portion 288 and surface 280.

A first motive power fluid port 294 is provided in body 264 to first chamber 290, and a second motive power fluid port 296 is provided in body 264 to second chamber 292. Hydraulic lines (not shown) are connected to each port, and conventional valves are connected to permit high and low pressure connections to be made. By admitting high pressure fluid to first chamber 290 piston 252 may be caused to advance; by admitting high pressure fluid to second chamber 292 piston 252 may be caused to retract or return, the size of the chambers expanding and contracting accordingly. In this arrangement, the outwardly extending portion or wall, 274, is, or functions as, the actuator piston or input interface piston 298. Assembly 250 further includes a controller 300, substantially similar in nature and operation to controllers 181 and 182, above. In this instance the position of second end 256 of piston 252 may be monitored by controller 300. Hydraulic pressure in the working fluid in chambers 290 and 292 can be modulated as above to produce a desired schedule of displacement as a function of time, and the forward stroke need not be equal in time to the rearward stroke, and so on, as above. In this operation, either the first end plate or the second end plate may be used as a stationary base or datum, or origin, or frame of reference.

In assembly 250, then, the fluid works against the annular surfaces of the actuator piston to produce displacement relative to the chosen datum surface or surfaces. Those surfaces are force input interfaces, and those force input interfaces are rigidly mounted, connected, positioned or oriented, relative to the output interface at first end 254. As before, piston 252 is restricted to a single degree of freedom of motion, namely linear reciprocation in the longitudinal direction. As before, there is no slack between the input and output interfaces of the moving members of the second compression stage. The difference is that the piston rod and connecting yoke, and their corresponding mass, has been eliminated, or rather replaced by an annular piston face, the remaining "transmission" between input and output, amounting to the annular portion or wall that carries the motive force in shear, and the cylinder wall itself, which carries the motive force in compression (when driving the work piece material), as a hollow short column in axial compression. The cylinder itself then become the common base structure, or common member, or common element linking, or shared by, both the actuator piston 296 and the output piston 254 - one common part thus carries both the input and output force transmission interfaces. I.e., the moving compression member includes both the input and output force transfer interfaces, and thus both the actuator piston and the compression piston, in one member. Alternatively, the continuous circumferential faces 282, 284 of the annular actuator piston can be thought of as being equivalent to a very large number of pistons operating around the circumference of the second compressor stage. Indeed, the annular piston need not be continuous, but could be an array of tabs of lugs at discreet circumferential intervals, e.g., three lugs spaced on 120 degree centers, four lugs spaced on 90 degree centers, and so on. A continuous annular chamber has the virtues of relative simplicity of construction, and automatic pressure equalization about the annular face. Operation

Piston 112 (or 252, as may be) is, or substantially approximates, a positive displacement device. It is also a device that may tend to impose the peak compression on the feedstock, and therefore the peak heat input. As such, the operation of piston 112 (or

252) may serve as a reference, or datum, for the operation of other components of processing apparatus 20.

In previous, passive, or passively controlled, apparatus, the rate of reciprocation of the second stage piston was not directly controlled. Rather, in one type of system, the pressure inlet valve for the advance stroke would open, and the piston would drive forward under the urging of the available hydraulic pressure at such rate as might be.

This might continue until a forward travel limit switch was tripped, at which point the forward travel input valve would close, and the return travel valve would open to cause the piston to reciprocate rearwardly. Alternatively, in a system with a flywheel and a crank, the piston would advance and retract as dictated by the turning of the motor and flywheel against the resistive pressure in the load. In the hydraulic ram system, then, neither the time v. distance nor the force v. distance profile was controlled or constant.

Among many possible outcomes of this kind of apparatus, there would be an instantaneous pressure surge in the work piece, which might lead to overheating or rubbing of the piston against the cylinder wall; on retraction the piston might tend to work against the main screw, with a resultant surge in power consumption.

By contrast, the use of a controlled time v. displacement schedule permits control over the pressure pulse applied to the work piece, and hence also to its heating. Further, since the apparatus may include feedback sensors for both piston 112 (or 252) and screw

76, the rate of advance of the screw, and hence its power consumption, can be modulated in real time in co-ordination with the operation of piston 112 (or 252). The piston feedback sensors may include sensors for monitoring position displacement and speed, force, hydraulic supply and return pressure, and hydraulic motor current. The drive screw sensors may include sensors operable to monitor angular position, displacement, speed, output torque, longitudinal thrust loading on the screw shaft, motor current, and motor shaft rotational position and displacement. For example, assuming that initial starting transients have been resolved, a steady pressurized wad of feedstock has been established in tail pipe 196, that pad also bearing against the choke cone 206, and that apparatus 20 is now running substantially at steady state. As piston 112 (or 252) is retracted, or is in the retraction stage of its operating cycle, the power to screw 76 may be reduced or held steady by decreasing the rate of advance of the screw. Then, in the forward or advancing portion of its operating cycle when piston 112 (or 252) and screw 76 are working in the same direction, and the action of piston 112 (or 252) may tend to unload screw 76, screw 76 may be advanced, i.e., turned, more rapidly. This control may be either an explicit control on the rotational speed of the motor, and hence of the screw, or it may be a control on motor current draw or a combination of the two. For example, there may be a scheduled speed of advance, provided that the motor current draw does not exceed a maximum value. In either case the system includes sensors operable to generate a warning signal and to move the system to a passive off-line, i.e., inoperative dormant status, in the event that either the force sensed at either piston is too high, or if the motor current exceeds a governed maximum. Inasmuch as the timing and displacement of the piston stroke are known, the operation of screw 76 may anticipate the motion of piston 112 (or 252) relative to and may itself be pre-programmed according to a pre-set schedule, with a suitable phase shift, as may be, or it may be adjustable in real time in response to observations of force and displacement of piston 112 (or 252). Similarly, rather than being passive, choke cone assembly 36 may be active. That is, rather than merely being subject to a fixed input force, be it imposed pneumatically or hydraulically; or a spring loaded input force such as imposed by a spring, all of which must be overcome by the piston to cause advance of feedstock into the main reaction vessel, choke cone assembly may be positively driven. That is to say, choke cone assembly 36 may be advanced an retracted either on the basis of a pre-set schedule, or in response to real-time feedback from piston 112 (or 252), and may be responsive to instantaneous load and rate of change of load as sensed at sensing assembly 212 (or 252). Thus, as piston 112 (or 252) advances, choke cone assembly 36 may be retracted somewhat to reduce the peak loading. When piston 112 (or 252) ceases to advance, and returns backward, choke cone assembly can be advanced to maintain a desired pressure level in the feed-stock pad. After processing through the reactor vessel, i.e., the digester, the feedstock is decompressed through the blow valve as described above.

By either or all of these features alone or in combination, active control of the displacement v. time and force v. time profiles may serve to reduce peak loading, to smooth the pressure profile over time in the feedstock, thereby reducing the tendency to local overheating, and tending to reduce the peak cyclic forces in the equipment, e.g., by reducing or avoiding spikes in the load history as a function of time. This may permit the use of a smaller motor, and may permit a lighter structure to be used. It may also reduce wear and damage to the equipment and may tend to reduce power consumption.

Various embodiments have been described in detail. Since changes in and or additions to the above-described examples may be made without departing from the nature, spirit or scope of the invention, the invention is not to be limited to those details.