FI59552B - PRESS INNEFATTANDE ETT FLERTAL PAO SKILDA AXLAR ROERLIGA PRESSVALSAR VARVID EN AV VALSARNA AER ROERLIG I SIDLED RELATIVT EN ANNAN - Google Patents

Description

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l J v 'UTLÄGGN INGSSKMFT ° y ° ^ · * ί? Χ5 C (4¾ Patent c / jnnetty 13'? 1331 ^ T ^ (51) Kv.ik.Wci. * B 30 B 9/20 FINLAND — FINLAND (21 ) PW * n «tlhak« mi · —PaMnciMahniiig 1569/72 (22) Hakunlipllvt — Ameknlnpdag 02.06.72 (23) Alku cloud— GlMgtimdkg 02.06.72 (41) Tullut JuIUmM — Mrlt affmtHg 23-12.72

PttMttti · jl rukitterlhullitut (44) NlhtivikslMnon it moonYulluJwn pvm. - och rugiaturutyrulMn '' Ainekin titled ech utl ^ krlftwi pubUemd 29.05.81. (32) (33) (31) hr4 · * 1 / ttuofktus — Suglrd reports 22.06.71 USA (US) 155UU1 (71) Improved Machinery Inc., Burke Street, Nashua, New Hampshire, USA (72) Sidney E. Stirk, Nashua, New Hampshire, John P. Rich, Nashua,

New Hampshire, Russell E. Holt, Candia, New Hampshire, USA (US) (7M Berggren Oy Ab (5 ^) A press comprising a plurality of press rollers rotating on different axes, one of which can move laterally with respect to the other -Press innefattande ett flertal pä skilda axlar rörliga pressval-sar, varvid en av valsarna är rörlig i sidled relativt en annan

The invention relates to a press comprising a plurality of press rolls rotatably mounted on different shafts, the circumferences of which are separated by a drain, one of which press rollers can move laterally with respect to the other to vary the width of the press tongue, two roller press devices for applying a first and a second press force. spaced apart in the longitudinal direction of the movable press roll and separately operable to apply a pressing force to the movable press roll and to allow lateral movement of the movable press roll away from the second roll, and a separate control device separately acting on the first and second press presses to apply the pressing force.

Conventionally, presses of this general type are used for many different applications, such as the compression of liquid suspensions such as pulp and waste sludge. In presses of this type for compressing liquid suspensions, at least one of the press rolls must be laterally movable relative to the other roll to vary the cross-sectional area of the throat Λ 2 S9552 so that even relatively large foreign bodies can pass through the throat to prevent expensive press rolls and / or other parts of the press. During the pressing operation, the center lines of the press rolls must also be kept parallel in order to harmonize the dryness of the exiting compressed material, to obtain a compressed web of uniform cross-section and also to effectively seal the roll ends, and to ensure satisfactory forced rotation of the lateral press roll. However, in conventional presses, in which the press rolls can move laterally with respect to each other, it is not possible to keep the center lines of the press rolls automatically parallel.

The main object of the present invention is to provide a novel and better press of the type described above, which is specifically constructed and adapted so that the center lines of the press rolls remain automatically parallel even if the press rolls can move laterally with respect to each other.

It is also an object of the invention to provide a new type of press of the type described above, which is specifically constructed and adapted so as to reduce the frictional phenomena which occur during its operation.

Other advantages of the invention will become apparent from the following description and the accompanying drawing, in which a preferred embodiment of the invention is shown for purposes of illustration.

The press according to the invention is characterized by what is stated in the characterizing part of the main claim.

In the drawing Fig. 1 is a vertical side view of a press comprising an embodiment of the invention, Fig. 2 is a vertical end view of the press of Fig. 1, Fig. 3 is an enlarged partial vertical side view in partial section, of the press of Figs. 1 and 2, Fig. 4 is a partial vertical sectional view of this press. of the press rolls, Fig. 5 is an enlarged partial perspective view of the press compression force application devices, Fig. 6 is an enlarged perspective partial view showing the second compression member of the force application device, and Fig. 7 is an enlarged partial vertical sectional view taken along line 7-7 of Fig. 5 in the direction of arrows.

In the drawing, in which the same reference numerals denote corresponding parts in all the different figures, Figures 1 to 7 show a press, 59552 comprising an embodiment of the invention, which is particularly suitable for pressing liquid suspensions such as pulp pulp or waste sludge. The press according to the drawing comprises a tank, i.e. a basin, generally indicated by reference numeral 10, both ends of which are supported by legs 12 standing on support trays 14. The basin has one or more cleaning hatches 16 through which its interior can be accessed for maintenance work. The basin 10 is provided with an inlet line 18 suitable for connection to a pressurized source of compressible suspension (not shown). The conduit 18 communicates with the bottom of the pool interior through a plurality of inlet pipes 20 and inlet ports 22 at the bottom of the pool. Connected to the basin 10 is an outlet line 24 which is open the entire length of the basin 10 to the top of the pool interior to receive compressed solids from the basin, and this outlet line 24 has a conventional feed coil 26 structured to disperse the compressed solids received and transport the disintegrated trough 24 down to its outlet 28. The feed coil 26 is attached to a rotating shaft 30 which also supports a conventional gear type speed reducer 32 having a pulley 34 on the shaft 36. The coil 26 and the shaft 30 are rotated by a speed reducer 32 by a conventional drive motor (not shown) and a drive belt 38 34 with each other.

Two pressure rollers 40, 42 are mounted for rotation about parallel axes in the basin 10 separated by a drain 44 between the rollers, which at its upper end communicates with the outlet line 24 and at its lower end with the inlet openings 22. The compression rollers 40, 42 are, as shown in Fig. 4, provided with roll-specific scraper blades 46, 48 which remove compressed solid from the circumferences of the rollers 40, 42 so that the removed material enters the feed coil 26 within the line 24. The rollers 40, 42 each have a plurality of axial directions. liquid or filtrate outlet passages 50 separated by ribs 52. The circumferential walls 54 of the rollers 40, 42 are perforated for draining liquid or filtrate into passages 50. The basin 10 is provided with filtrate drain lines 58 for draining liquid from passages 50 at each end of press rolls 40, 42. At each end of each roll 40, 42 there is a curved sealing device (not shown) to prevent leakage from the area of the ends of the rolls.

Flexible sealing devices (not shown) along the axes of the rollers are also adapted to seal the basin in the longitudinal direction of the rollers 40, 42.

* 59552

The hubs 56 of the press rolls 40, 42 have pin shafts 60 integral with the roll, projecting from the ends of the rolls and on which the ends of the rollers 40, 42 are mounted on two support devices 62, respectively. 64. The support devices 64 are fixed so that the roller 42 they support can rotate about a stationary axis. The support devices 62 can slidably move toward and away from the support devices 64, moving the roll 40 they support laterally toward and away from the roll 42, thereby varying the cross-sectional area of the throat 44. Each support device 62 is attached to one end of an upper and lower tie rod 66 which slide slidably through holes in the support devices 64 and whose other ends are on the opposite side of the roll 40 to the roll 42. A compression plate 68 is attached to the ends of the tie rods 66 attached to both support devices 62. that the plates 68 can move sideways together with the support devices 62 and the roll 40 they support.

On opposite sides of the drain 44 are air-expandable springs, i.e. tubes 70, between support devices 62, 64 at each end, and apply forces to the support devices 62 to move the roll 40 away from the roll 42. The expanding tubes 70 are each connected to a relatively large common pressure by their own air inlet 72 to a source 74 in which the pressure is constant. Thus, the expanding tubes 70 apply equal constant forces to the support devices 62 and the roll 40 they support.

The rollers 40, 42 are rotated in opposite directions of rotation, schematically shown by the arrows in Figures 3 and 4, a drive device including a rotating main drive shaft 76 adapted to be coupled to a conventional rotary drive motor (not shown). The main drive shaft 76 is in communication with one of the pin shafts 60 supporting the pinch roller 42 via a conventional gear generally located within the housing 78. The pin shaft 60 at the opposite end of the roll 42 is in communication with an adjacent pin shaft 60 supporting the roll 40 via a conventional gear within the gearbox 80. The interlocking teeth of the gears in the gearbox 80 are so deep that the roller 40 and its pin shafts 60 can have limited movement relative to the roller 42 and its pin shafts 60 without interrupting the drive connection between the pin shafts 60 of the rollers 40, 42.

The compressive force is applied to the roll 40 by the pressing devices 82, 84 of the two articulated systems 5 59552, which are laterally spaced apart in the longitudinal direction of the roll 40 and act on this roll by means of plates 68, tie rods 66 and support devices 62. The roll pressing devices 82, 84 are completely similar in structure and arrangement to provide the same mechanical effect, and include joints that are oriented and proportioned so as to provide a substantially uniform throat pressure regardless of the throat cross-sectional area. As best seen in Figures 3 and 5, each device 82, 84 includes a substantially vertical joint, a first joint 86 having an articulation pin 88 between the ends of which the joint 86 is articulated to a stationary bracket 90. The lower end of each first joint 86 is articulated by a pivot pin 92 a substantially horizontal ✓ second joint, i.e., one end of the association joint 94, the other end of which is connected by a hinge pin 96 to the lower end of the substantially vertical, bifurcated third joint 98. As shown in Figures 5 and 7, the openings 118 in the joints 94 for the pivot pins 96 are larger in vertical length than the cross-sections of the pivot pins 96. The pivot pins 96 are vertically centered in the openings 118 by springs 120 and prevented from rotating by wedges 122. Thus, the pivots 94 are in rolling contact with the pivot pins 96 so that the connection between the pivots 94 and the pivot pins 96 is low friction.

The upper ends of the third joints 98 are articulated to the stationary brackets 100 by articulation pins 102, and each have a hinge 104 of the same piece which is substantially S-shaped in vertical cross section. These substantially S-shaped joints 104 are articulated in contact with compression members 106 and compression plates 108 fitted to the upper and lower recesses 110, 112 of the joints 104, respectively, and attached to support devices 64 and compression plates 68, respectively. pressing devices 82, 84 to their respective adjacent plates 68 and apply the pressing forces of the devices 82, 84 to the roll 40. As shown in Fig. 6, flat springs 114 are attached to the pressing pieces 106 by a tensioner 116 to center the pressing pieces 106 in their recesses 110, 112.

The roll pressing devices 82, 84 are actuated by device-specific, pressure medium-operated control devices 124, one of which is shown in Figure 3. The control devices 124 each comprise a pitch cylinder 126 having a piston 128 provided with an extension arm 130 connected by a pivot pin 132 to the respective device 82. or 8h to the upper end of the first joint 86. The pivot pin 132 and the pivot pins 88, 92 described above are each provided with circumferential needle bearings or the like to reduce friction at the contact points. Due to the way in which these needle bearings and the pivot pins 96 described above engage the joints 9, the sensitivity of the devices 82, 84 to variations in the feed rate of the suspension passing through the throat 44 has been maximized. Each cylinder 126 is articulated to a stationary support 13. The piston rod ends of the cylinders 126 are connected by cylinder-specific medium lines 136 to a relatively large common source, i.e., a tank 138 with a constant pressure pressure medium such as air. The reservoir 138 is connected to a line 14'0, which in turn communicates with an outlet line 142 that opens into the atmosphere. Between the lines 140, 142 is a valve, generally indicated at 144, along lines 140, 142 to control the outlet pressure medium. The valve 144 includes a piston 146 which tends to be pushed by a spring 148 to an open position where lines 140, 142 communicate with each other to remove compressed air from reservoir 138. Piston 146 normally tends to compress a closed position where communication between lines 140, 142 is blocked. comes down the inlet line 150 with the control valve 152. The valve 152 is normally controlled by the solenoid 154 to bring the line 150 of the valve 144 into contact with the source of pressure medium, but when power is lost from the solenoid 154, the spring 156 causes it to release the pressure medium from the valve 144 to the outlet line 158 , the spring 148 being able to move the piston 146 to its above-mentioned open position. A switch, generally designated 110, attached near one of the third joints 98 after the latter movement of a predetermined length to be triggered is electrically connected to the solenoid 15 by an electrical conductor 162 to turn off the solenoid 15 when the switch trips. The cylinder head of each cylinder 126 is provided with an outlet line 164 for rapidly releasing the medium from the cylinder.

The roll pressing devices 82, 84 are connected to each other by an adjusting device which adjusts the devices 82, 84 so as to cause the latter to keep the axis of the pressing roll 40 parallel to the axis of the roll 42. As best seen in Figure 5, 7 59552, this adjusting device comprises a torsion bar 166 rigidly connected at both ends to the first joints 86 of the devices 82, 84, concentric with the pins 88. Thus, the torsion bar 166, as will be explained below, as the joint 86 of the second device 82 or 84 moves, moves the same movement to the joint 86 of the second device, thus ensuring that the axes of the rollers 40, 42 remain parallel.

During normal operation of the press, the expanding tubes 70 are filled with compressed air from the source 74 and apply constant, equal forces via support devices 62 to the ends of the roll 40, keeping the latter sink 44 separate from the roll 42. The piston rod ends 146 is closed when solenoid 154 is energized. The pistons 128 of the guide devices 124 cause the pressing devices 82, 84 to apply a pressing force to the ends of the roll 40 through the tie rods 66 of the pressing plates 68 and the support devices 62. Thus, the throat 44 becomes compressed. Due to the structure and arrangement of the joints of the pressing devices 82, 84 described above, and since the air pressure in the cylinders 126 of the control devices 124 is constant, a uniform compressive force remains in the throat regardless of the width of the throat 44. The pressure rollers 40, 42 are continuously rotated by the drive shaft 76 via gears in the gearboxes 78, 80. The liquid suspension to be compressed is continuously fed to the lower end of the basin 10 along the supply line 18 and the supply pipes 20 and through the supply openings 22. The pressure of the fed suspension causes some of its liquid content to flow through the circumferential porous walls 54 of the rollers 40, 42 into the inner channels 50 of the rolls, and as the suspension passes through the sink 44 between the rollers 40, 42 the rest of the suspension liquid content is squeezed out and flows through the circumferential walls 54. the solids are removed from the rollers 40, 42 by scrapers 46, 48 and the rotating feed coil 26 delivers it along the discharge line 24. The liquid in the discharge channels 50 drains out of them up to the filtrate drain lines 58.

Throughout the normal operation of the press, the axis of the roll 40 remains parallel to the axis of the roll 42, and the compressive force exerted by the pressing devices 82, 84 on the roll 40 (and thus the drain 44) remains compressed by the drain 44 at a substantially constant force regardless of nip cross-sectional area. In the event that foreign objects pass through the nip from any point other than the center of its length, the movement of the end of the roll 40 closest to this foreign body away from the roll 42 automatically and substantially simultaneously causes equal movement of the joints of the presses 82 or 84 at the corresponding end, which in turn substantially immediately causes the torsion bar 166 to cause the same movement in the second compression device 82 or 84. The low friction bearing of the joints 86, 94, 98 and the bar 130 greatly reduces the effect of friction on the movement of the joints. The compressed air at the piston rod end of the cylinders 126 of the control devices 124, of course, flows to the tank 138 due to the movement of the pistons 128 thus caused.

It follows that the axes of the rollers 40, 42 remain parallel substantially throughout the normal operation of the press. By keeping the rollers 40, 42 on parallel axes, the cross-section of the compressed material remains uniform over the entire length of the nip 44, the seals at the ends of the rolls 40, 42 are not damaged, and the gears connecting the rollers 40, 42 remain parallel, so that any damage is prevented.

In the event that the roll 40 moves away from the roll 42, as may occur due to too much or variable suspension feed or very large foreign bodies passing through the throat 44, the switch 160 is triggered by a third joint 98 adjacent to it, disconnecting the solenoid 154. As a result, the spring 156 moving the valve 152 so as to allow compressed air to flow along the outlet line 158 so that the spring 148 can move the piston 146 of the valve 144 to its open position, the reservoir 138 communicating with the outlet line 142, and compressed air discharged from the cylinder heads 126 of the control device 124. Thus, the compression normally provided by the pressing devices 82, 84 ceases so that the roll 40 can move away from the roll 42 and any significant damage is prevented. The switch 160 may also, if desired, be suitably electrically connected so as to prevent the suspension from continuing to flow into the throat 44, and / or otherwise stop the press, e.g. by stopping the rotation of the rollers 40, 42.

It will be apparent from the above description that the invention provides a novel, improved device which achieves all the objects and advantages listed above. Although only one embodiment of the invention has been described above, the invention is not limited to this single embodiment, but encompasses other embodiments within the scope of the appended claims.

Claims (15)

A press comprising a plurality of press rolls (40, 42) rotatably supported on separate shafts and circumferentially spaced by a nip (44), one (40) of the press rolls being laterally movable relative to another (42). varying the width of the press nip (44), a first and a second roller pressure device (82, 84) for exerting the pressing force, which devices are longitudinally separated from the movable press roll (4o) and which are individually actuated to exert the compressive force on the the movable press roll (40) and allow a lateral movement of the movable press roll (40) away from the second press roll (42), and a separate actuator (124) which individually actuates the first and second roll press means (82, 84) to exerting the compressive force, characterized in that, as connecting elements between the roller pressure devices (82, 84), torsion bars (166) which are fixedly connected to corresponding links (86) in the system with the roller pressure devices function, that the torsion bars are coaxial. a with a fixed shaft (88) about which the links (86) are pivotally arranged, that the torsion bars (166) are spaced apart from the axis of the movable press roller (40) and are separate from the actuator (124), and that the torsion bars (166) are arranged to transmit the movement from the first roller pressure device (82) to the second (84) and vice versa to tilt the axes of the press rolls (40, 42) in parallel. Press according to claim 1, characterized in that the connecting elements (166) extend in the longitudinal direction of the movable press roll (40). Press according to Claim 1 or 2, characterized in that the first and second roller pressure devices (82, 84) comprise separate linkage systems. Press according to claim 3, characterized in that each link system (82, 84) comprises a plurality of links (86, 94, 98, 104). Press according to Claim 4, characterized in that the parts of each link system in each link system are interconnected by means of low friction connections. Press according to any of claims 1-5, characterized in that the connecting elements consist of a torsion bar (166). Press according to any one of claims 1-6, characterized in that the actuator (124) comprises individual, pressure-fluid actuated actuators for the roller presses (82, 84), and control means (144, 152, 160) which are arranged for movement of moving the movable press roll (40) away from the second press roll (42) causes the pressure fluid to be emptied from the actuators. Pressure according to claim 7, characterized by a common pressure fluid source (138) for supplying pressure fluid to the actuators, the control means (144, 152, 160) also causing the pressure fluid to be discharged from said pressure fluid source. Press according to any of claims 3-8, characterized in that each link system comprises a pivotally mounted first link (86) connected at one end to one of the actuators, a second link (94) pivotally connected to the other end of the first link. (86), a third link (98) is pivotally connected to the second link (94) and a fourth link (104) is connected to the third link (98) and exerts the force on the movable press roller (40). Press according to claim 9, characterized in that the fourth links (104) have a substantially S-shaped cross-section. 11. Press according to claim 10, characterized by low friction joints connecting the S-shaped links to the movable press roll (40) and to a fixed support (68). Press according to any preceding claim, characterized by load means (70) between the press rolls (40, 42) which push the movable press roll (40) away from the second press roll (42). Press according to claim 12, characterized in that the loading means comprise several pressure fluid driven actuators and a common source (74) for pressure fluid supply to said actuator. Press according to any of claims 12 or 13, characterized in that the load means (70) are arranged adjacent opposite sides of the press nip. Press according to any preceding claim, characterized by support means (62) at opposite ends of the pipe.