FI57798B - RAFFINATOR MED DUBBELFLYTSKIVOR - Google Patents

Description

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Patent · och ragiatantyralaan 'AmMcm uttagd ocfc gtukruten pubuemd 30.06.80 (32) (33) (31) Requested «uoikws-Bagird priority 17 · 07.71 * USA (US) 1 + 89 ^ 16 (71) Koppers Company, Inc., Koppers Building, Pittsburgh, Pennsylvania 15219, ^ USA (72) Chester Donald Fisher, Muncy, Pennsylvania, Beatrice Pearl Fuller,

Muncy, Pennsylvania, USA (7 ^) Leitzinger Oy (5 ^) Cleaner with two floating discs - Raffinator med dubbel-flytskivor

The invention relates generally to disc-type wood chip cleaners and in particular to a high-speed double cleaner with rotating double floating discs.

Disc-type cleaners are well known in the papermaking industry in particular and include substantially parallel annular cleaning surfaces arranged to rotate relative to each other so that the material to be cleaned fed to the inner edge of the surfaces enters the surfaces by centrifugal force and leaves the circumference in the cleaned space. Cleaners generally include either one pair of cleaning surfaces or, in the case of dual cleaners, a double pair of cleaning surfaces. One type of cleaner with one pair of cleaning surfaces is known as a rotatable and axial fixed cleaning head that cooperates with an axially adjustable, rotating head. In another simple type of cleaner, the heads rotate against each other, with one being axially fixed and the other axially adjustable. In addition, one type is known for a rotating end that is axially fixed and a non-rotating end that includes means for axial adjustment to change the clearance of the cleaning plate.

2 57798

Dual cleaners typically include a central rotating head with abrasive plates on each side that cooperates with oppositely positioned, rotatably fixed plates. One or both of the ends supporting the fixed plates may be axially adjustable to change the clearance of the plates, and the shaft supporting the rotating head may be either axially adjustable or free-bearing. U.S. Patent 3,276,701 discloses an example of a free-bearing type double disc cleaner in which the second fixed end is axially adjustable, and this patent has been transferred together with this application to a common assignee.

As the size of the cleaners increases, the thrust forces generated by the cleaning operation become quite large. Today, cleaners with plate diameters of more than 120 cm and horsepower of more than 1000 are being built. Known double-disc cleaners have largely eliminated the problem of axial forces on the rotating shaft, and this is especially true of the type of disc disc cleaners disclosed in U.S. Pat. . However, the difficulty with a float-type double cleaner is the risk of uneven feed of raw material as a result of the movement of the float head and likewise the possibility of the plates colliding. In addition, such unevenness can cause at least momentary, strong thrust forces on the shaft, and suitable bearings must be provided in the event of such a possibility.

The present invention provides a dual cleaner having a pair of non-rotating, axially immovable fixed ends and a pair of axially adjustable rotating heads interposed therebetween. The cleaning plates attached to the fixed and rotating ends cooperate in a known manner and perform an abrasive action on the material passing between them. Each of the rotating ends is attached to sleeves which slide axially on the drive shaft and are rotated by a central drive disc on the drive shaft, which includes drive lugs extending on each side thereof, which engage the respective lugs on the rotating heads. The sleeves supporting the rotating heads are axially positioned by means of a cylinder-piston member connected to a parallel hydraulic circuit, whereby the impulse forces generated by the rotating heads are equalized. The members associated with the cylinder-piston member limit the axial movement of the rotating heads and prevent the possibility of the plates colliding, thus enabling the cleaner to operate under unloaded conditions with a predetermined clearance between the cleaning plates.

Accordingly, it is an object of the invention to provide a new and improved high speed double disc cleaner for cleaning wood chips and the like which is substantially more economical to build and maintain than conventional cleaners and includes rotating double float discs which minimize the thrust forces of the cleaning shaft, thus allowing very light shafts.

This object is achieved by a purifier according to the appended claim 1.

It is a further object of the invention to provide a double disc cleaner as described, comprising means for limiting the sliding rubber movement of the rotating discs to prevent the cleaner plates from colliding and to allow the cleaner to be used even under unloaded conditions. Structural solutions that serve this purpose are reflected in the sub-requirements.

Other objects and advantages of the invention will become more apparent from the following detailed description of an embodiment of the invention taken in conjunction with the accompanying drawings, in which: Figure 1 is a side elevational view of a purifier constructed in accordance with the invention; Figure 2 is an elevational view of the right end of the cleaner shown in Figure 1; Fig. 3 is an enlarged sectional view taken along line 3-3 of Fig. 2 showing the interior details of the purifier; Fig. 4 is an enlarged fragmentary sectional view, with a portion cut away, showing a section of the right-hand cylinder-piston arrangement shown in Fig. 3 for positioning the right-hand rotating disk; Fig. 57798 is a sectional view taken along line 5-5 of Fig. 3; and Fig. 6 is a partial plan view taken along line 6-6 of Fig. 3 showing the manner in which the drive disc lugs interact with the rotating disc lugs.

Referring to the drawings, and in particular to Figures 1-3, a cleaner according to the invention, generally indicated by reference numeral 10, includes a base 12 supporting spaced apart separable housing portions 14 and 16. The central housing portion 18 is releasably secured between portions 14 and 16. to provide access to the cleaner plates. The housing part 18 may comprise a pair of curved parts which are tightened between the housing parts 14 and 16 by bolts 20 connecting the parts.

The bearing support portions 22 and 24 extend outwardly from the housing portions 14 and 16, respectively, to rotatably support the cleaner drive shaft 26, which extends through the housing portions. As shown in Fig. 3, the contour of the left end of the drive shaft 26 is stepped and mounted on a bearing unit 27 fixed inside the bearing support portion 22. The drive shaft is axially positioned by a bearing unit 27 located against the drive shaft shoulder 28 and held against the shoulder by a locking ring 30 threadedly attached to the drive shaft. The bearing unit 27 implanted in the bore 32 with the shoulder of the cylindrical support member 34 is secured in place by an annular locking member 36 and a locking ring 38 tightened by screws 40. Seals 42 and 44 at opposite ends of the bearing unit 27 prevent foreign matter from entering the bearings. The bearings shown are of the angular contact type which dampen light impulsive forces, although the cleaner should not, in normal use, generate any such impulse forces which would need to be damped by the bearings of the cleaner shaft.

At the opposite end of the cleaner, the drive shaft is supported by a bearing support part 24, inside which a cylindrical support part 46 is fixed. The radial bearing unit 48 is attached to the shoulder bore 50 of the member 46 and secured in place by a ring 52. Sealing units 54 and 56 are provided on each side of the bearing unit 48.

5 57798

The surfaces of rotation of the housing parts 14, 16 and 18 are located around a shaft 26, the shaft of which is assumed to be the shaft of the cleaner. The circular openings 58 and 60 at the respective ends of the housing parts 14 and 16 allow the shaft 26 to pass through. As can be seen in particular from Figure 2, the base 12 is provided with a curved contoured surface 62 on which the housing parts 14 and 16 are slidably supported. Although the housing parts are bolted together during operation of the cleaner, for inspection or replacement of the plate, the housing parts 14 and 16 can be axially moved to the positions 14 'and 16' shown in broken lines in Figure 3. To move the housing parts to the open position by the latches 64a and 66a, the piston-cylinder units 64 and 66 attached to the base are coupled to the housing portions 14 and 16, respectively, to slide the housing portions into the base on the curved surface 62 to provide the required axial force.

The housing portions 14 and 16, which are frustoconical in shape as shown in Figure 3, respectively include non-rotatably axially fixed ends 68 and 70 arranged circumferentially with respect to the drive shaft. The ends are annular and are attached to the housing portions at their outer radial edge and at their inner radial edge they are attached to raw material inlet conductors 72 and 74 spaced concentrically spaced around the drive shaft 26. The cleaner plate units 76 and 78 are attached to opposite radial surfaces of the ends 68 and 70, respectively. Each cleaning plate unit includes a conventional system of cleaning plate elements, such as those disclosed in, for example, U.S. Patent 3,473,745, which is assigned to the assignee with this application.

The drive disk 82 is mounted on the drive shaft 26 in a radially aligned central position equidistant from the fixed ends 68 and 70. The drive disk 82 includes a plurality of equally spaced lugs 84 extending axially on each side of the disk circumference as shown in Figures 3 and 6.

The rotating ends (also referred to as discs) 86 and 88 are located on opposite sides of the drive disc 82, respectively, and are aligned with the non-rotating ends 68 and 70, respectively. The rotating ends 86 and 88 are generally annular in shape and are respectively attached to sleeves 90 and 92 which cover the drive shaft 57798 26 tightly but axially slidably relative thereto. The rolling ends 86 and 88 and the sleeves 90 and 92 then attached thereto are rotated by the drive disk 82 by means of lugs 94 and 96 extending from the ends 86 and 88, respectively, and engaging the drive disk lugs 84. This lug arrangement causes the rotating ends to rotate with the drive shaft, but it allows axial movement of the drive shaft because the lugs of the rotating ends can slide axially along the lugs of the drive disc.

The cleaning plate units 98 and 100 are attached to the rotating ends 86 and 88, respectively, adjacent to the cleaning plate units 76 and 78 of the fixed ends 68 and 70, respectively. In the normal operating position of the rotating heads, the cleaning plate units 98 and 100 are slightly separated from the fixed cleaning plate units 76 and 78 to provide an abrasion effect on the raw material passing between them.

The distance between the plates is controlled by adjusting the position of the sleeves 90 and 92 as shown below.

The raw material supply units 102 and 104 are respectively attached to the housing parts 14 and 16. Since the feed conveyors 102 and 104 are substantially identical except for the direction of rotation of the conveyor screws, only the conveyor unit 104 will be described in detail. Referring to Figs. 2 and 3, the conveyor unit 104 extending from the vertical, flanged inlet conduit 108 outside the housing portion 16 to a downwardly directed discharge chute 110 located within the housing portion vertically above the shaft of the cleaner. The outlet shaft 110 communicates with an opening 112 in the cylindrical housing portion 74. A conveyor screw 114 attached to the inside of the conveyor shell 106 is rotated by a motor 116 connected thereto by a chain drive unit 118 as shown in FIG. Accordingly, the conveyor screw 114 conveys the raw material fed to the inlet line 108 to the outlet chute 110 and passes through the opening 112 in the member 74 to the annular partitioned chamber 120 between the sleeve 92 and the member 74. A similar chamber 122 is formed at the opposite end of the purifier and fed to the conveyor unit 102 in the same way as the conveyor unit 104. The conveyor screws rotate so as to guide the raw material towards the rotating ends 86 and 88, and then, as shown in Fig. 3, the conveyor screw 114 rotates clockwise while the screw of the conveyor unit 102 rotates counterclockwise.

7 57798

From the raw material supply chambers 120 and 122 to the cleaner throats 124 and 126, respectively, located adjacent to the cleaner plate units, is provided by a conveyor member having a plurality of triangular lugs 128 rotating with the drive shaft and extending into chambers 120 and 122. Triangular lugs 128 are thus positioned , that their angularly directed surfaces direct the raw material towards the cucumbers 124 and 126 regardless of the direction of rotation of the drive shaft. The reversibility of the drive shaft is an important factor to allow even wear of the abrasive elements of the cleaner plates. The lugs 128 are preferably arranged at regular intervals in axially aligned rows, the lugs of each row being axially alternately or interleaved with respect to the lugs of adjacent rows. The lugs 128 are attached to sleeve extensions 90a and 92a located on the sleeves 90 and 92 and extending axially beyond them.

The lugs 128 allow steam generated during the cleaning process to pass back through the raw material to the steam removal lines 130 and 132, which pass vertically through the housing portions 14 and 16, respectively, at their outer ends. A reversible ear conveyor structure head as described is similar to that disclosed in Patent Application 296,564, which has been assigned together with this application to a common assignee. Although this is a preferred raw material conveyor structure due to its reversibility, a belt screw cleaner feeder such as that disclosed in U.S. Patent 3,441,227 may also be used, which has also been transferred to a common transferee with this application. Both of these conveyors allow the necessary backflow of steam, which is generated during the purification of a very thick raw material.

The cleaned material passes between the sets of cleaning plates into an annular chamber bounded by a central housing portion 18, fixed ends 68 and 70, and rotating ends 86 and 88. Some cleaned material may get between the drive disk 82 and the rotating discs 86 and 88, although most of the cleaned material thrown into the circumferential regions of the chamber 134 due to centrifugal force. An outlet line 136 in communication with the annular chamber 134 passes through the substrate 12 to remove the purified feedstock.

The hydraulic system for axially positioning the rotating ends 86 and 88 57798 includes a coaxial bore 138 in the drive shaft 26 extending from the left end of the shaft 26, looking at Figure 3, to a position approximately flush with the outer end of the housing portion 16. The bore 138 includes a pair of cylindrical plugs 140 and 142 located in the vicinity of the outer ends of the sleeves 90 and 92, respectively. Since the structure and operation of both plugs 140 and 142, as well as the passageways in the drive shaft adjacent to the plugs, are substantially the same, only the plug 142 and the hydraulic passageways shown in an enlarged view in Fig. 4 will be explained in this connection.

The bore 138 is provided at its open end with threads 144 for connection to a source of pressurized fluid (not shown). The hydraulic fluid in bore 138 passes through openings 146 in plugs 140 and 142, thus filling bore 138 along its entire length. Radial openings 148 and 150 connect bore 138 to chambers 152 and 154, which pistons 156 and 158, respectively, form adjacent the drive shaft 26, the pistons being helically attached to the drive shaft and flanged ends 160 and 162 of flange extensions 90a and 92a. Supplying pressurized hydraulic fluid to chambers 152 and 154 tends to move the rotating ends axially toward the drive disk 82 and thus away from the fixed ends, thereby increasing the plate clearance.

The sheathed end cover members 168 and 170 form chambers 164 and 166 on the outside of the pistons 156 and 158, which cover members are attached to the flanged ends 160 and 162 of the sleeve extensions 90a and 92a, respectively. The end cover members 168 and 170 are in intimate contact with the drive shaft 126 and consequently that the supply of pressurized hydraulic fluid to the chambers 164 and 166 causes an outward movement of the settling or floating ends, which reduces the plate clearance. The pressurized hydraulic fluid is supplied to the chambers 164 and 166 through oblique openings 172 and 174, respectively, which openings engage the bore 138 at the plugs 140 and 142 and communicate with the ring 176. According to Figure 4, each ring 176 communicates with a radial opening leading to the plug axial opening 180. With 178. A line 182 extending axially through the bore 138 is threadedly connected to the plug to cooperate with the axial bores therein. Line 182 terminates in a threaded connector 184 for connection to a pressurized hydraulic source (not shown).

9 57798

A hydraulic arrangement as described to control the axial position of the rotating plates is essentially a piston-cylinder arrangement in which the pistons are fixed and the cylinders move relative to the fixed pistons. The movement of the rotating heads 86 and 88 is limited in the closing direction by stop rings 186 and 188, respectively, which are helically adjustable by the drive shaft and locked in the desired position by locking screws. The flanged stop nuts 190 and 192 threadedly attached to the end caps 168 and 170 limit the opening movement of the rotating ends 86 and 88, respectively.

For the operation itself, the drive shaft 26 of the cleaner is connected by means of an extension 26a of the shaft to a power source which is normally a fairly large electric motor, for example 1000 horsepower. The feed inlet lines are connected to a source of feedstock to be cleaned, which feedstock typically flows by gravity from an upstream location to feed conveyors 102 and 104. The drive shaft bore 138 and line 182 are connected to appropriate sources of pressurized hydraulic fluid via control and valve means. connect one channel to the outlet pipe while the other is connected to a source of pressurized fluid.

The feed conveyors 102 and 104 are rotated at a predetermined speed to provide a steady flow of raw material to chambers 120 and 122. The raw material is guided into the cucumbers 124 and 126 by triangular lugs 128 and progresses centrifugally between the cleaning plates in a known manner. The purified material exits the chamber 134 through an outlet pipe 136. During the cleaning process, the generated steam passes through the chambers 120 and 122 and exits through the discharge lines 130 and 132. Although the steam travels against the feed of the raw material, the raw material is thrown against the outer walls of the chambers 120 and 122 by centrifugal force, thus allowing the steam to pass along the inner walls of the chamber without disturbing the flow of the raw material.

The control of the plate clearance is achieved by means of cylinder-piston units which operate in parallel and adjust the position of the axially rotating heads 86 and 88. The supply of pressurized hydraulic fluid to the chambers 152 and 154 while the chambers 164 and 166 open to the outflow causes the clearance of the plates to increase. Conversely, the supply of pressurized hydraulic fluid to the chambers 164 and 166 and the emptying of the chambers 152 and 154 reduce the clearance of the plates. Since the chambers shown are connected in parallel to the sources of hydraulic pressure, the rotating ends 86 and 88 move freely, i.e. "float" on the drive shaft 26, and are positioned so that the forces generated between the two sets of cleaning plates are equal because the opposing forces produced by each piston-cylinder unit are equal in size.

The use of a parallel hydraulic system to adjust the clearance of the plates causes the piston rings 156 and 158 to be pushed evenly and counterclockwise during operation of the cleaner. Because the wiper shaft dampens this thrust, no special shaft thrust bearings are needed except those that are necessary to support potential loads. Given the huge amount of horsepower currently used in twin cleaners, the omission of large thrust or thrust bearings and their maintenance results in significant savings over a conventional cleaner design.

A preferred feature of the rotary end cylinder-piston control is the stop arrangement, which absolutely prevents the plates from colliding, even if the cleaner is operated without a raw material flow. The stop rings 186 and 188 are helically adjusted to their position and locked to the drive shaft, so that the end caps 168 and 170 engage the stop rings, respectively, before the wiper plates collide.

Likewise, the stop nuts 190 and 192 provided with flanges limit the amount by which the wiper plates can differ from each other because the flanges of the stop nuts adhere to the stop rings at a predetermined position.

It will be apparent to those skilled in the art that changes may be made in the details of the structure without departing from the spirit and scope of the invention.

Claims (12)

A disc type refiner with a base (12), a housing (14, 16, 18) supported by the base, a drive shaft (26) running through the housing, means (27, 48) arranged on the housing for supporting the drive shaft rotatably, within the housing, pairs of stationary heads (68, 70) mounted spaced from and opposite one another, a refiner disk unit (76, 78) disposed on both stationary heads and a center on the drive shaft (26) between said stationary heads (68, 70) drive disk (82), thereby rotating other refiner disk units (98, 100) which are in cooperation with the refiner disk units (76, 78) of the stationary head, and transport means (102, 104) for guiding raw material intended for refining into said housing next to said refiner disk units, characterized in that it further has a pair of rotatable heads (86, 88) attached to the drive shaft (26) which are located on opposite sides of said drive disk (82), means (84; 94). , 96) connecting the drive disc (82) and the rotatable heads (86, 88) t, said heads rotate together with the drive shaft simultaneously permitting their axial movement along said axis, the other refiner disk units (98, 100) being secured to each of said rotatable heads (86, 88) side by side with the adjacent stationary heads. refiner disk units (76, 78), and means (152, 156, 164; 154, 158, 166) for adjusting the axial position of the rotatable heads (86, 88) on the drive shaft (26), the latter means being provided with a piston cylinder device connected to the rotatable heads and a hydraulic circuit which joins the said coupling by means of parallel coupling. the piston cylinder means for balancing the adjusting force directed against the rotatable heads (86, 88), thus permitting "liquid" axial movement of the rotatable heads for balancing the force of the hydraulic cylinder piston unit against that between the refiner disc units (76, 98 or 78, 100) ) developed the axial force. Device according to claim 1, characterized in that the two rotating heads (86, 88) are coupled with a sleeve (90, 92) arranged to concentrically and axially slide along the drive shaft (26). 3. Apparatus according to claim 2, characterized in that the cylinder piston device in contact with the rotating heads 57798 (86, 88) comprises a piston (156j 158) attached to the drive shaft (26) and a coiled surrounding cylinder (152, ISA ·). 164, 166), which connects to the sleeve of the rotating head (90, 92). 4. Apparatus according to claim 2, characterized in that it comprises lines (138, 182) for hydraulic fluid in the drive shaft (26) which are connected to the cylinder chambers (152, 164; 154, 166) on both sides of the coil. (156, 158), wherein the hydraulic fluid pipes are connected in parallel such that similar fluid pressure is simultaneously directed at corresponding chambers (152, 154 and 164, 166) of both piston cylinder devices. 5. Device according to claim 1, characterized in that the conveying means (104, 102) for controlling raw material to the chamber, which is adjacent to the refining disk unit, have a cylindrical raw material channel (120, 122) which is concentric to the drive shaft (26) and is located on it. said sleeve (92; 90), and that transport members (128) are attached to each sleeve and said transport means (104, 102) comprise a screw conveyor (114) for feeding raw material into said raw material channel or conduit (120; 122). 6. Device according to claim 5, characterized in that the said sleeve transport elements (128) belong to several radially extending ears, wherein each ear has a pair of transverse surfaces, which are opposite at an angle obliquely to the drive shaft, the edge of the ear formed by said transverse surfaces, is directed toward the adjacent rotating head (86, 88). 7. Apparatus according to claim 5, characterized in that there is also a meadow drain line (130, 132) for removing meadow from the bed mentioned raw material lines (122; 120), wherein said meadow sewer line has been arranged axially vented at the distance from said screw conveyor ( 114). 8. Device according to claim 2, characterized in that it has means (186, 168, 190; 188, 170, 192) for limiting the axial movements of said rotating head (86, 88).