GB1597614A

GB1597614A - Sorting apparatus

Info

Publication number: GB1597614A
Application number: GB1298178A
Authority: GB
Original assignee: Xerox Corp
Current assignee: Xerox Corp
Priority date: 1977-04-04
Filing date: 1978-04-03
Publication date: 1981-09-09
Also published as: JPS53123937A; FR2386468A1; JPS6119537B2; DE2812624A1; FR2386468B1

Description

(54) SORTING APPARATUS (71) We, XEROX CORPORATION, of Xerox Square, Rochester, New York, United States of America, a Corporation organised under the laws of the State of New York, United States of America, do hereby declare the invention, for which we pray that a patent may be granted to us, and the method by which it is to be performed, to be particularly described in and by the following statement: This invention relates to sorting apparatus particularly for collating the output of a reproducing machine into one or more sets and to reproducing machines incorporating such apparatus.

Numerous sorting apparatus are known in the prior art for collating the output of reproducing machines into a desired number of sets. For example U. S. Patent Nos.

3,774,902; 3,848,868 and 3,990,695 describe sorting apparatus having a vertical array of generally parallel horizontally extending inclined sorter trays, the sheet being delivered to the trays by a sheet transport system comprising a horizontal transport leading to a vertical transport.

The present invention is concerned with providing access to the interiors of sorting apparatus such as those described above for maintenance and the removal of jammed sheets. U. S. Patent No. 3,990,695 above and No. 3,973,769, show the use of a vertical transport which, for access, is arranged to pivot away from the main sorter frame which supports the respective bin defining trays.

In accordance with the invention, there is provided a sheet sorting apparatus in which first and second frames, which respectively support a plurality of sheet receiving bins and a transport for transporting sheets towards the bins, are arranged for relative movement between a first, closed position in which the sheet transport is operatively associated with the bins and a second, open position in which the sheet transport and the bins are separated for access, and in which a guide mounted on the second frame for guiding sheets along the sheet transport is moved away from the sheet transport when the frames are separated to their open position to facilitate removal of sheets from between the transport and the guide.

In one embodiment the guide is closely spaced adjacent the sheet transport in the first frame position and is spaced further apart from the transport in the second frame position. Such a guide is sutaMy a pivotally mounted plate extending across the sheet transport which in the first frame position is inclined towards the sheet transport in the direction of sheet movement.

Where the sheet transport includes one or more tensioned belts, sheet removal may be facilitated by reducing the belt tension. In an embodiment in which the guide is arranged to form a nip with the belt(s), the movement of the guide away from the belt reduces the belt tension whereby the nip force between the belt and the guide is reduced.

In order that the invention may be more readily understood, reference will now be made to the accompanying drawings, in which: Figure 1 is a schematic representation of a reproducing apparatus and sorting apparatus of this invention, Figure 2 is a partial section view of the sorting apparatus, Figure 3 is a rear view of the sorting apparatus, Figure 4 is a front view of the sorting apparatus, Figure 5 is a partially cut away sectional view of the sorting apparatus, Figure 6 is a partial perspective view of the inner-vertical transport and sheet deflection system of the sorting appraratus, Figure 7 is an inside view of the vertical transport door of the sorter apparatus, Figure 8 is a partial side view of the bin and sheet deflector bin actuation system of the sorter, Figure 9 is a partial rear view of the sorter motor drives system, Figure 10 is a partial rear view showing the timing belt tensioning system for the sorter transport drives, Figure 11 is a perspective view showing an adjustable cam follower, Figure 12 is a perspective view of a ribbed type transport roller, Figure 13 is a partial front view in crosssection of a portion of the vertical transport door showing operation of the turn roll and sheet baffle camming in the sorter, Figure 14 is a partial perspective view of the sorting apparatus showing operation of the vertical transport door counterbalance, Figure 15 is a rear view of a sorting apparatus in accordance with a different embodiment of this invention having ten bins.

Referring to the drawings, Figure 1 shows the manner in which a sorting apparatus 11 according to the invention may be embodied in a reproducing machine. Specifically it is embodied in an automatic xerographic copier 10 although it will be understood that sorting apparatus of this invention may be incorporated in other forms of reproducing machine, or may comprise a separate module attachable to a reproducing machine or a stand-alone machine.

The reproducing machine 10 illustrated in Figure 1 employs an image recording drum 12 supporting a suitable photoconductive material 13 and mounted on a shaft 14 for rotation in the direction indicated by arrow 15 to bring the photoconductive surface 13 past a plurality of xerographic processing stations in synchronisation with their operation.

The drum 12 moves the photoconductive surface 13 past (a) a charging station 17 where it is uniformly charged, (b) exposure station 18 wherein the charged surface 13 is exposed to a light image of the original input scene information whereby the charge is selectively dissipated in the light exposed regions to record the original input scene in the form of a latent electrostatic image, (c) development station 19 wherein coloured toner particles are applied to the surface 13 to render the latent image visible, (d) a transfer station 23 where the developed image is transferred to sheet 16 of final support material, e.g. paper, which is supplied from tray 20 is registration with the image by means of a sheet separator 21 and sheet registration system 22, and (e) a cleaning station for removing from the surface 13 residual toner particles remaining following the transfer step.

After the toner image has been transferred thereto the sheet 16 with the image thereon is advanced to a suitable fuser 24 which coalesces the transferred power image thereto.

After the fusing step the sheet 16 is advanced to a suitable output device such as tray 25.

Referring now to Figures 1--7, the sorter 11 is arranged adjacent the output of the xerographic processor. As a sheet 16 exits from the fuser 24, it is carried by the processor output rolls 27 along the horizontal sorter transport 30. A deflection gate or pivoting chute 31 is arranged selectively to deflect the sheet 16 from the horizontal sorter transport 30 into the output tray 25 or to allow its continued advancement along the horizontal transport. When the chute 31 is in its up position as shown in solid lines in Figure 2, the sheet 16 exits from the output rolls 27 and falls into the output tray 25 which is inclined downwardly toward the process 10. O-rings 33 are arranged about the lower output roll 27 and an adjacent idler roll 34 positioned below the lower output roll.

The function of the O-rings 33 is to aid in stacking the sheets in the output tray 25 by driving the trail edge of the sheets downwardly into the tray. When sorting is desired, the deflection chute 31 is moved to its down position, as shown in phantom in Figure 2, so that the sheets are fed along the horizontal transport 30 of the sorter 11. The deflection chute is actuated by means of a solenoid 35.

Driven pinch rollers 40 are arranged at an intermediate position along the horizontal sorter transport 30. These rollers are driven to advance the sheet at about the speed of the output rolls 27. The lower rollers 41 are pinned to driven shaft 42. The upper rollers 43 idle on shaft 44. A lever actuated jam detection switch 45 is provided following the rollers 40 for detecting jams, in the horizontal sorter transport.

The upper sheet guides 46 and 47 comprise wire forms which are pivotally supported in the main sorter frame 50 about shafts 51 and 52 as shown in Figure 3. Levers 53 supported at the outer ends of the shafts 51 and 52 limit the pivotal motion of the guides 46 and 47 for jam clearance thereby preventing them from being left open during operation.

As a sheet 16 proceeds further along the horizontal transport 30, it is fed into the nip formed by turn roll 60 and drive belts 61.

Upon exiting the nip the sheet 16 is guided by pivoting baffle 62 onto the vertical transport 63 of the sorter 11. The drive belts 61 are driven at high speed as compared to the horizontal transport rolls 40 so that upon the copy sheet being gripped in the nip between the turn roll 60 and the drive belts 61, it is pulled at a high speed from the nip of the horizontal transport rolls 40. In order to accomplish this, the driven lower rolls 40 are driven through an overrunning clutch 64 such that the rollers 40 can be overridden by the drive imparted to the sheet 16 by the vertical transport drive belts 61.

The vertical transport 63 is composed of a plurality of pinch roll sets 70. One set of pinch rolls being arranged adjacent each of the bins 71 of the sorter 11. A plurality of spaced apart drive belts 61 are arranged across the width of the sorter from front to back. They are carried about idler pulleys 72 and 73 so that inner-run 74 of the belts 61 wrap around the turn roll 60 to provide driving engagement with a sheet nipped therebetween. The inner-run 74 of the belts 61 runs through the nips of each of the pinch roll sets 70. The pinch rolls comprising the sets 70 are arranged to idle on their respective shafts 75. A drive pulley 76 is provided at the lower end of the vertical transport 63 for providing a drive input to the belts 61. The drive belts 61 provide the driving engagement with the sheet 16 as it is carried along the vertical transport 63. The inner-pinch rolls 77 are supported in the main sorter frame 50. The outer pinch rolls 78 are supported in a frame assembly or door 80 which is arranged to pivot away from the main sorter frame 50 in order to allow access to the vertical transport 63 sheet path forjam clearance by the operator.

The vertical sorter bin array is composed of a plurality of sorting trays 81 arranged in a parallel fashion, one above the other, to provide a vertical row of bins. Each bin 71 is defined by the sheet receiving tray 81. The first bin 71A has a desired operating width for handling the desired number of copy sheets to be collected in it. The last bin 710 of the sorter 11 has a comparable width. The width of a bin 71 is defined from the sheet supporting surface 82 of the tray 81 to the bottom surface 83 of the next adjacent tray.

The intermediate bins 713-I and K-N have a width which is less than the width of the first and last bins.

The sorting system 11 shown comprises 15 bins, however, as will be described later by reference to Figure 15, the sorter has a modular construction which allows the total number of bins to be cut down to 10 bins, if desired, for low volume applications. This 10/15 bin modularity is accomplished by utilizing a 10th bin 71J which has the same width as the first and last bins 71A and 710.

For the 10 bin version of the sorter, that 10th bin 71 J becomes the final bin.

The use of intermediate bins 71 B-I and K-N which are closely spaced together provides a high degree of compactness.

For purposes of further explanation, the wider bins 71A, J and 0 will be described hereafter as full width bins and the narrower bins 71 B-I and K-N will be described hereafter as compact bins. Each of the bins 71 is adapted to hold approximately the same number of sheets.

Associated with each of the bins 71, except the last bin 710 are a series of deflection gates 90 each supported upon a shaft 91 journaled in the sorter frame 50. A plurality of deflection fingers 92 are supported in a spaced apart relationship along each shaft 91 to define the respective gates 90. The deflection fingers 92 are arranged to project between the respective pinch rolls 77 which are also spaced apart along their respective shafts 75, as shown in Figure 6. A stationary deflection chute 95 is used to guide a sheet 16 into the last bin 710.

The compact bins 71 B-I, and K-N are articulated such that their bin entrances can be selectively widened as a sheet is fed into them. This is accomplished by providing levers 93 secured at the end of the deflection gate shafts 91, which operate against the bottom surface 83 of the tray 81 defining the top of the respective bin 71 with which the shaft 91 is associated. The levers 93 selectively operate upon the trays 81 outside the sheet path to cam them upwardly in order to widen the bin entrance opening as a sheet is fed into the bin.

End of the trays 81 of the sorter 11 except for the top tray 25 which acts as the nonsorting output tray for the reproducing machine 10 and the bottom tray which rests on the sorter frame 50 are supported in a pivotal fashion within the sorter frame 50. Tabs 100 are provided at one end of the trays 81. The tabs 10 are positioned through slots in the sorter frame 50 to pivotally support the trays therein. Removable retaining pins 101 are placed through holes in the tray tabs 100 in order to retain the trays within the frame 50.

The articulated trays 81 are arranged so that their other end is supported by the camming levers 93. The non-articulated trays 81, namely, the top trays associated with each of the full width bins 71 J and 0 are arranged so that their free ends rest against pins 102 supported in the sorter frame 50 as in Figure 4.

While camming levers 93 are present on the deflection finger shafts 91 associated with the full width bins 71 A, J, and 0, they are not required, since the arc through which they sweep does not result in their engagement with the bottom of the tray 81 above the bin with which they are associated. They are included in the apparatus only because the deflection gate assembly 90 which includes the levers 93 is easier to fabricate as a common unit for each of the bins 71.

Each of the deflection gate shafts 91 is extended through the rear of the sorter frame 50 and includes at its extended end an adjustable follower element 104.

The bin indexing drives 110 for the sorter 11 are best shown by reference to Figures 2, 3, and 8. The deflection gate 90 for the first bin 71 A is arranged to be actuated by means of a solenoid 111. The armature 112 of the solenoid 111 is connected to the outboard end of the deflection gate shaft 91 by means of a fork-shaped coupling element 113. The shaft 91 of the first deflection gate is the only shaft which does not include a follower element 104. Compression spring 115 urges the first gate 90 closed when the solenoid 111 is not actuated.

The solenoid 111 is connected to the sorter control system (not shown) and is actuated in sequence for a time period sufficient to deflect a sheet 16 from the vertical transport 63 into the first bin 71A. The use of a solenoid actuated deflection gate 90 for the first bin 7 IA allows the sorter 11 to be recycled for receiving the first sheet of the next page being copied without reference to the position of the cam drive system 120 which sequences the deflection gates 90 of the remaining bins 71.

Each of the remaining deflection gates 90 is controlled by means of a modular cam drive system 120 supported in the rear side frame 50 of the sorter 11. A plurality of stub shafts 121 are provided for supporting cam units 122 for actuating each deflection gate 90 in sequence by operating on its respective follower element 104. Each cam unit 122 comprises a cam portion 123 and a gear portion 124. The cam elements are alternately arranged such that the cam portion 123 of one cam unit 122 is situated on one side of the respective gear portion 124 of that element while the cam portion 123 of the next adjacent unit 122 are situated on the opposite side of their respective gear portions 124. The high points of the cam portions 123 are arranged to sequentially actuate the deflection gates 90 for the bins 71 by engagement with the follower elements 104. The gear portions 124 of the respective cam units 122 for the bins 71 B through 711 are intermeshed. Similarly, the gear portions 124 of the cam units 122 for bins 71J through 71N are also inter-meshed. There is no connection between the gears 124 associated with cam units 122 for bins 71I and 71J. This allows the bin array to be modular so that, if desired, the bottom 5 bins can be removed at a substantial cost savings. The 10 bin modification will be described later by reference to Figure 15.

An input drive pulley 125 is rotatably supported about shaft 127 and is connected to the upper cam units 122 through a coaxially gear portion 128 which meshes with the gear portion 124 of the cam unit for the 8th bin 71 H. A second input drive pulley 130 is rotatably supported about shaft 131 and is connected to the lower cam units 122 through a coaxial gear portion 132 which meshes with the gear portion 124 of the cam unit for the 14th bin 71N. The input drive pulleys 125 and 130 are driven by respective timing belts 133 and 134 connected about respective first and second drive output pulleys 135 and 136 mounted to output shafts 137 and 138. The shafts 137 and 138 are suitably journaled and mounted to the sorter frame 50. Spur gears 141 and 142 are mounted to the shafts 137 and 138 via the input side wrap spring clutches 139 and 140, as shown by reference to Figure 9, and are arranged to mesh with motor drive gear 143.

The wrap spring clutches 139 and 140 include respective detent collars 144 and 145 including three saw tooth-like detents arranged 120 apart. Solenoids Sl and S2 actuate pawls 147 and 148 to selectively disengage them from the detent collars 144 and 145 to increment the deflection gate drive.

During sorter operation the motor 150 is continuously driven as are the respective drive gears 141, 142, and 143. Intermittent motion is applied to the output drive pulleys 135 and 136 by selective operation of the solenoid actuated pawls 147 and 148. Each time a solenoid S1 or S2 is actuated, it momentarily lifts its pawl 147 or 148 and allows 120 of rotation of its respective output timing belt pulley 135 or 136. This 120 of rotation is translated by means of a 3:1 timing belt pulley ratio into a 40 rotation of the cam units 122. Due to the meshed gear arrangement 'of the cam bank, alternating adjacent cam units 122 rotate in the opposite direction. However, for each actuation of a solenoid S1 or S2 the cam units associated therewith rotate 40 . Therefore, for the upper cam bank which includes eight cam units 122, a series of nine solenoid S1 actuations returns the cam bank to its home position, namely, provides a full 360 of rotation of the cam units 122.

The home position of each cam bank is set by means of a home switch 151 or 152 which senses a pin 153 or 154 associated with the cam unit 122 of the upper cam bank for bin 71 B or with the cam unit 122 of the lower cam bank for bin 71L.

In operation when the cam banks are in their home positions and sorting is selected, solenoid 111 actuates the deflection gate 90 for the first bin 71A. A sheet sensor 159 comprising light 160 and photodetector 161 are arranged to detect a sheet 16 entering any of the bins. After the sensor 159 detects that a given sheet has entered bin 71A, the upper cam bank is advanced 40 by actuation of solenoid S1 to cause the deflection gate 90 associated with the second bin 71 B to enter the sheet path. As the upper cam bank indexes from its home position to the second bin 71 B operative position the deflection gate shaft 91 associated with the second bin is rotated by operation of the first cam element 122 against the follower element 104 supported by the shaft. This causes the deflection gate 90 for the second bin 71 B to move into the sheet feed path to deflect the next fed sheet into the second bin. As soon as the second sheet is sensed to have entered the second bin 71 B, the upper cam bank is again indexed so that the next sheet will enter the next bin in line, etc., until sheets are received in the first nine bins 71A--71I.

The lower cam bank home position is selected so that the deflection gate 90 for the 10th bin 71J, which is controlled by the first cam unit 122 of the lower cam bank is normally in its operative position to deflect a sheet from the vertical transport 63. Therefore, to feed the 10th sheet into the 10th bin 71J, the upper cam bank is indexed to its home position wherein none of the gates 90 associated therewith are operative. Solenoid 111 is not actuated so that the deflection gate 90 associated with bin 71A is inoperative.

Upon sensing the 10th sheet entering bin 71J the lower cam bank is advanced 40 to open the 11th bin 71K deflection gate 90 to deflect the 11th sheet thereinto. This sequence is then repeated until the 15th bin 710 receives its sheet.

Since the upper cam bank has proceeded through a full cycle, it has been returned to its home position. The lower cam bank is also incremented in 40' intervals in order to provide commonality for the components of both cam banks. Therefore, upon completion of the 14th sheet entering the 14th bin 71 N the lower cam bank is not in its home position. The lower cam bank is then recycled by continuous actuation of the second solenoid S2 until switch 152 senses the home position pin 154 of the lower cam bank.

The operation which has been described thus far involves the full utilization of all of the bins 71. A feature of the appartus described herein is that the first bin 71A is independently controlled. This is an important feature since it overcomes the difficulty in recycling the upper cam bank between copy sheets if only two sets are sorted, as will now be described.

The first two sheets are sorted as described above. The solenoid actuated gate for bin 71A is opened for the first sheet to enter the first bin and then closed. The cam bank then is indexed to open the gate for the second bin 71 B to accept the second sheet into the second bin. The next sheet which is received from the processor 10 is intended for the first bin 71A.

The control system (not shown) provides a signal to the pawl actuating solenoid S1 to recycle the upper cam bank to its home position. However, the time involved to provide such recycling is greater than the time it will take for the next sheet to get to the first bin 71A. This is not a problem in the sorting appartus herein since the first bin 71A is operated independently of the remaining bins 71 B-I which are cam driven.

Therefore, the first bin gate 90 can be returned to its open position for stripping the next sheet as the upper cam bank is being recycled to its home position.

For any desired number of sets from 1-8 or 10--15, the respective cam banks are not in their home positions after receiving the last sheet of a given page and, therefore, they must upon sensing the last sheet be recycled to their home positions by continued actuation of their respective solenoids S1 and S2 until actuation of the respective home switches 151 and 152. The lower bank is operated only when sorting eleven or more sets, since the deflection gate 90 for the 10th bin 71J is open when the lower cam bank is in its home position.

The drive input to the cam banks is at a relatively high speed in order to reduce the time necessary to index the cams between sheet receptions. The cams must be indexed in the time that is allowed between sheet receptions. This inter-document time is extended by means of the high speed drive imparted to the sheets 16 by the vertical transport 16 which increases the pitch or distance between incoming sheets. This allows sufficient time for the cams to index so that the deflection gate 90 for the bin receiving the next sheet to be opened as the deflection gate of the previous bin closes.

The follower elements 104 as in Figure 11 comprise a first member 156 secured to the respective shaft 91 and a second member 157 pivotally supported about the shaft and connected to the first member by set screw 158. The set screw 158 can be used to adjust the operative position of the deflection gate 90. While the pinch rolls 70 are shown as comprising flat rolls they are preferably ribbed as in Figure 12 in accordance with known practice.

The drives for the vertical transport belts 61 and for the horizontal transport rolls 40 are taken off the continuously driven gear 142 by means of a gear 161 meshed therewith as shown in Figure 9. The gear 161 is mounted to the shaft 162 which supports the drive pulleys 76 for the vertical transport belts 61 and, therefore, directly imparts the drive to those belts.

A timing belt pulley 163 as in Figure 3 is secured to the end of the drive shaft 162 to provide a drive connection for the horizontal transport rolls 40. A drive direction reversal timing belt tensioning system 170 as in Figures 3 and 10 is provided at an intermediate position. A first plate 171 is adjustably supported by the frame 50 by screws 172. A stub shaft 173 is mounted to plate 171 and corotating gear 175. A timing belt 176 is supported about pulleys 163 and 174. A second plate 177 is pivotally supported about shaft 173 and adjustably secured to plate 171 by screws 178. A stub shaft 179 is mounted to plate 177 and rotatably supports a timing belt pulley 180 and corotating gear 181 which meshes with gear 175 to reverse the drive direction. A timing belt pulley 182 is mounted via over-running clutch 64 to the lower roll drive shaft 42 of the horizontal transport rolls 40. A timing belt 183 wrapped about pulleys 180 and 182 completes the drive connection to the horizontal transport roller 40.

The belt tension of the respective belts 176 and 182 is adjusted by means of the plates 171 and 177 to which the pulleys 174 and 180 are mounted. The first belt 176 tension is adjusted by moving the inner plate 171 which is then locked in position by the screws 172. The second belt 183 tension is then set by pivoting the plate 177 and pulley 180 about the axis of the first pulley shaft 173 and then locking it in place to the inner plate 171 by means of screws 178. In this manner, the belt tensions for the timing belts 176 and 180 can be easily set without concern for the meshing engagement between the respective gears 175 and 181.

The tensions of timing belts 133 and 134 are set using adjustable idler rolls 185 and 186, respectively. The normal force between the pinch roll sets 70 is provided by cantilever springs 187 supported by the door frame 80 and urged against the ends of the shafts 75. The follower elements 104 are loaded against the cams 123 by the weight of the trays 81 acting on the levers 93. The 10th bin 71J follower element 104 is loaded against the cam 123 by a torsion spring 189.

Referring to Figures 1-7, and 13, its noted that the outer bank of vertical transport pinch rollers 78 and the drive belts 61 are arranged in a door-like frame assembly 80 which can be pivoted away from the main sorter frame assembly 50 which supports the inner pinch rollers 77 deflection gates 90. The door 80 is arranged to pivot about the input drive shaft 162, which thereby makes it unnecessary to disconnect the belt drives when the door is pivoted open. Folding links 190 are pivotally supported between the door and main sorter frame in order to prevent the door from falling completely open and for limiting the degree to which the door can be opened.

A latch mechanism 191 as in Figure 2 is provided for holding the door 80 closed during normal operation. The latch 191 is comprised of a pivotal member 192 which includes hook portion and a lever portion.

The member 192 is biased about stub shaft 193 by means of a spring 194. A catch pin 195 is arranged in the main sorter frame 50 and is engaged by the hook portion of member 192 when the door 80 is closed. To open the vertical transport door 80 the lever portion of the member 192 is merely pulled back by the operator to lift the book away from the pin 195 and thereby allow the door to swing open. A similar latch (not shown) is provided at the opposing side.

The sorter assembly 11 is itself arranged for easy engagement and disengagement from the reproduc the nip force between it and the belts. The turn roll 60 isjournaled at each end in sliding shoes 210, which in turn are supported in sliding engagement in respective slots 211 in each end of the door frame 80. The sliding shoes 210 include tabs 212 which engage adjustable stop pins 213 on the door frame 80 to limit the amount of travel of the turn roll 60 in the direction away from the belts 61.

The shoes 210 also include a follower surface 214 which is arranged to engage a ramp 215 secured to the main sorter frame 50. The portion of Figure 13 in solid lines shows the vertical transport door 80 in its operative position for sorting. The ramp 215 comprises an inclined ramp with a flattened or level portion. When the door is fully closed the follower surface 214 of the shoes 210 rests on the level portion of the ramp 215. In this position the roll 61 defelects the feed belts the maximum amount and the tension of the feed belts is set at a high value which is desired for sheet handling. When the door 80 is swung open, as shown in phantom in Figure 13, the slide shoes 210 carry the roll 60 downwardly and outwardly of the door frame to lower the roll and to decrease the amount of deflection of the feed belts 61 thereby substantially reducing the forces between the feed belts and the roll. The travel of the feed roll 60 is limited by the aforenoted engagement of the tabs 212 on the respective slide carriages 210 with the pins 213 attached to the sorter door frame 80. By reducing the tension on the feed belts 61 by reducing their deflection through the movement of the turn roll 60 as aforenoted, it is possible to easily clear jammed sheets from between the turn roll and the feed belts.

Still referring to Figure 13, a second feature of the turn roll assembly is shown which comprises a sheet guide baffle 62. This guide baffle 62 is arranged to insure that a sheet 16 as it exits the nip between the turn roll 60 and the feed belts 61 is properly fed into the nip between the first set of pinch rollers 70. In solid lines the baffle 62 is shown in its operative position wherein it defines at its upstream end a relatively wide gap between it and the belts 61 for intercepting a sheet coming out of the turn roll nip, and at its downstream end a relatively narrow gap for guiding a sheet into the nip of the first set of pinch rolls 70. The narrow gap makes it difficult to clear a sheet jammed between the turn roll 60 and the feed belts 61 if one is pulling from below the turn roll. In order to alleviate this difficulty the guide baffle 62 is supported by pivot arms 220 at each end thereof which in turn are arranged to pivot about the shaft 221 of the turn roll. A torsion spring 222 is arranged with one end pinned to the slide shoe 210 and the other end pinned to an arm 220 of the pivoting baffle 62 so as to urge the baffle to a normally opened position as shown in phantom. In the open position of the baffle 62 the gap between it and the belts 61 is widened to allow easy jam clearance. Closure of the baffle 62 or its pivotaly movement to its operative position as shown in solid lines is accomplished by means of a follower tab 223 attached to it which in turn engages a camlike member 224 which is secured to the main sorter frame 50. As the door is closed, the follower tab 223 of the pivoting baffle 62 engages the stationary cam 224 and is caused to pivot to its operative position as shown in solid lines. The engaging surfaces of the tab 223 and cam 224 are shaped as shown to provide a progressive camming action which as the roll 60 rises results in a generally sinusoidal motion of the baffle 62 required to clear the first bin 71A deflection gage 90. The tab 223 operative surface comprises an inclined plane with a curved tip. The cam 224 operative surface is curved convexly.

Another jam clearance feature of the sorter 11 comprises flanges X provided at the ends of belt pulleys 72. These flanges have a large diameter so that they extend above the belt 61 surfaces. Therefore, when a sheet 16 is withdrawn from the nip between the belts 61 and turn roll 60 it is slid against the flanges X of the pulleys 72 rather than the high friction surfaces of the belts supported thereabout.

This reduces the drag on the sheet 16 as it is pulled from the nip.

Referring now to Figures 3, 7 and 14, the counterbalance mechanism 230 used to counterbalancem the vertical transport door 80 when it is pivoted away from the main sorter frame 50 is shown. The counterbalance mechanism comprises two leaf springs 231 mounted in cantilever fashion to the main sorter frame 50 by screws 232. The free end of each leaf spring includes a curved lip 233.

The door 80 itself includes a roller 234 at each end which is preferably formed of nylon or a similar material. The rollers 234 are supported for rotation about stub shafts 234 mounted to the door frame 80. These rollers 234 engage the leaf springs 231 so that as the door is opened the rollers ride along the springs toward the lips 233. The leaf springs 231 are secured to the main sorter frame 50 by means of plate members 236. The plate members 236 include a flared portion. The plate members 236 control the deflection of the springs 231 as they are counterbalancing the door to prevent over-stressing the springs.

The action of the rolls 234 against the leaf springs 231 allows the leaf springs to counterbalance the door 80. As the door 80 is opened the springs 231 are deflected as the roll rides along the spring surface. In this manner effective counterbalancing of the door 80 is provided which prevents sudden shocks to the machine 10 as the sorter door 50 is opened.

Referring now to Figures 5 and 15, a ten bin version of the sorting apparatus 11' of the present invention is shown in detail. As indicated previously, the sorting apparatus described is of a modular construction and can be provided with any desired number of bins 71 and in particular it can be provided so that it can have one number of bins or alternatively a somewhat larger number of bins. This is accomplished in a single vertical array. If ten bins are used they are aligned vertically, and if fifteen bins are used they are also aligned vertically.

In order to accomplish this modularity the tenth intermediate bin 71J is arranged to be a full width bin as aforenoted. The deflection gates 90 for the tenth bin 71J and through the 15th bin 71 N of the 15 bin sorter are driven by means of the lower cam bank, as shown in Figures 3 and 8. If only a ten bin sorter is desired, the lower cam bank, deflection gates 90 for bins 7 IJ to 7 IN, the drive gear 141, the wrap spring clutch 139, the solenoid S1 and pawl 147 can all be eliminated.

The drive for pulley 125 is taken from the drive pulley 136 previously used to power the lower cam bank. A timing belt 240 is wrapped about pulleys 125 and 136. The control signals previously applied to solenoid S1 in the fifteen bin version 11 are applied to the solenoid S2 in the ten bin version 11'.

In the ten bin version 11' there is no need for this deflection gate 90 for the 10th bin 71J, since the deflection chute 95 of the 15th bin 710 is moved up to the 10th bin position.

Therefore, in converting to 10 bins from 15 bins there is no necessity to change the upper cam bank for driving the deflection gates, since they are driven in the same manner as in 15 bin version 11 described above. Therefore the sorting apparatus is modularly constructed so that the number of bins in the sorting array can be selectively changed as desired without over complicating the drive system. A high degree of commonality is achieved between ten bin configuration 11 and the fifteen bin configuration 11. The other elements of the ten bin configuration 11 are the same as described by reference to the fifteen bin configuration 11.

The sorter control system does not form a part of the present invention and any desired control system may be used to provide the desired control and sequencing signals necessary to operate the sorters 11 or 11'. It is only necessary to feed the first bin operable signal to solenoid 111 and the remaining bin operable signals to solenoids S1 and S2, respectively, to provide the desired sequencing.

As described herein above the drive system wherein the first bin in the sorting array is driven independently of the remaining bins of the array and wherein the remaining bins are driven by a sequential cam drive system eliminates throughput reductions associated with sorting low numbers of sets. This is particularly important when the copies includes a document handling system 250 as in Figure 1, which is arranged to place documents on and off the viewing platen. With such a system it is possible to maintain the full throughput of the copies even with document change and it is not necessary to delay the copying cycle after document change because of the necessity to recycle the sorter cam banks to their home positions.

WHAT WE CLAIM IS: 1. Sheet sorting apparatus in which first and second frames, which respectively support a plurality of sheet receiving bins and a transport for transporting sheets towards the bins, are arranged for relative movement between a first, closed position in which the sheet transport is operatively associated with the bins and a second, open position in which the sheet transport and the bins are separated for access, and in which a guide mounted on the second frame for guiding sheets along the sheet transport is moved away from the sheet transport when the frames are separated to their open position to facilitate removal of sheets from between the transport and the guide.

2. Apparatus according to claim 1, including a said guide which is spaced closely adjacent the sheet transport in the first position of the frames and is spaced further apart from the transport in the second position of the frames.

3. Apparatus according to claim 2, wherein the guide comprises a pivotally mounted plate extending across the sheet transport which in the first position of the frames is inclined towards the sheet transport in the direction of sheet movement.

4. Apparatus according to claim 1,2 or 3, in which the sheet transport includes at least one belt under tension and, to facilitate removal of sheets from the sheet transport, the belt tension is reduced in the second position of the frames compared with its tension in the first position of the frames.

5. Apparatus according to claim 1, 2 or 3, in which the sheet transport includes at least one belt under tension and in which there is provided a said guide which is arranged to form a nip with the at least one belt, the movement of the guide away from belt reducing the belt tension whereby the nip force between the belt and the guide is reduced.

6. Apparatus according to claim 5, wherein the belt tensioning guide comprises a roll.

7. Apparatus according to claim 6, wherein a plurality of spaced apart said belts are arranged each to form a nip with roll.

8. Apparatus according to claim 6 or 7,

**WARNING** end of DESC field may overlap start of CLMS **.

Claims

**WARNING** start of CLMS field may overlap end of DESC **. Referring now to Figures 5 and 15, a ten bin version of the sorting apparatus 11' of the present invention is shown in detail. As indicated previously, the sorting apparatus described is of a modular construction and can be provided with any desired number of bins 71 and in particular it can be provided so that it can have one number of bins or alternatively a somewhat larger number of bins. This is accomplished in a single vertical array. If ten bins are used they are aligned vertically, and if fifteen bins are used they are also aligned vertically. In order to accomplish this modularity the tenth intermediate bin 71J is arranged to be a full width bin as aforenoted. The deflection gates 90 for the tenth bin 71J and through the 15th bin 71 N of the 15 bin sorter are driven by means of the lower cam bank, as shown in Figures 3 and 8. If only a ten bin sorter is desired, the lower cam bank, deflection gates 90 for bins 7 IJ to 7 IN, the drive gear 141, the wrap spring clutch 139, the solenoid S1 and pawl 147 can all be eliminated. The drive for pulley 125 is taken from the drive pulley 136 previously used to power the lower cam bank. A timing belt 240 is wrapped about pulleys 125 and 136. The control signals previously applied to solenoid S1 in the fifteen bin version 11 are applied to the solenoid S2 in the ten bin version 11'. In the ten bin version 11' there is no need for this deflection gate 90 for the 10th bin 71J, since the deflection chute 95 of the 15th bin 710 is moved up to the 10th bin position. Therefore, in converting to 10 bins from 15 bins there is no necessity to change the upper cam bank for driving the deflection gates, since they are driven in the same manner as in 15 bin version 11 described above. Therefore the sorting apparatus is modularly constructed so that the number of bins in the sorting array can be selectively changed as desired without over complicating the drive system. A high degree of commonality is achieved between ten bin configuration 11 and the fifteen bin configuration 11. The other elements of the ten bin configuration 11 are the same as described by reference to the fifteen bin configuration 11. The sorter control system does not form a part of the present invention and any desired control system may be used to provide the desired control and sequencing signals necessary to operate the sorters 11 or 11'. It is only necessary to feed the first bin operable signal to solenoid 111 and the remaining bin operable signals to solenoids S1 and S2, respectively, to provide the desired sequencing. As described herein above the drive system wherein the first bin in the sorting array is driven independently of the remaining bins of the array and wherein the remaining bins are driven by a sequential cam drive system eliminates throughput reductions associated with sorting low numbers of sets. This is particularly important when the copies includes a document handling system 250 as in Figure 1, which is arranged to place documents on and off the viewing platen. With such a system it is possible to maintain the full throughput of the copies even with document change and it is not necessary to delay the copying cycle after document change because of the necessity to recycle the sorter cam banks to their home positions. WHAT WE CLAIM IS:

1. Sheet sorting apparatus in which first and second frames, which respectively support a plurality of sheet receiving bins and a transport for transporting sheets towards the bins, are arranged for relative movement between a first, closed position in which the sheet transport is operatively associated with the bins and a second, open position in which the sheet transport and the bins are separated for access, and in which a guide mounted on the second frame for guiding sheets along the sheet transport is moved away from the sheet transport when the frames are separated to their open position to facilitate removal of sheets from between the transport and the guide.

8. Apparatus according to claim 6 or 7,

wherein said roll is arranged for sliding movement within said second frame, whereby said roll slides between its respective first and second positions.

9. Apparatus according to claims 3 and 6, wherein the guide plate is pivotally supported by the belt tensioning guide roll and is arranged to move with the roll.

10. Apparatus according to claim 5 in which the belt is entrained over a pulley, the belt tensioning guide is arranged in nipped engagement with the belt adjacent the pulley and means is provided for reducing the drag on a sheet as it is pulled about the pulley from the nip between the belt and the guide.

11. Apparatus according to claim 11, wherein the drag reducing means comprises flanges on the pulley which extend radially beyond the belt.

12. Apparatus according to any preceding claim, wherein movement of said guide to its operative position is effected by a cam on the first frame and a cam follower connected to the guide, the follower engaging the cam as the frames are closed together.

13. Apparatus according to claim 12, wherein the cam and follower are provided with engaging surfaces which provide a progressive camming action as the first and second frames are closed together.

14. Apparatus according to claim 13, wherein the cam and follower surfaces are arranged to provide by said progressive camming action a generally sinusoidal motion to said guide plate.

15. Apparatus according to claim 14, wherein the engaging surface of the follower comprises an inclined plane and the engaging surface of the cam is curved convexly.

16. Apparatus according to any preceding claim, wherein the second frame is pivotally supported by the first frame for movement between the first and second frame positions.

17. Apparatus according to claim 16, including at least one cantilever spring for counterbalancing the second frame as it is moved.

18. Apparatus according to claim 17, wherein the second frame includes means for engaging the cantilever spring and the cantilever spring is mounted to the first frame.

19. Apparatus according to claim 18, wherein the means for engaging the cantilever spring comprises a roller rotatably supported by the second frame, and the spring has a convexly curved surface for engagement by the roller.

20. Sheet sorting apparatus constructed, arranged and adapted to operate substantially as hereinbefore described with reference to Figures 1 to 14 of the accompanying drawings.

21. Sheet sorting apparatus constructed, arranged and adapted to operate substantially as hereinbefore described with reference to Figure 15 of the accompanying drawings.