WO2015045142A1 - Dispositif de pliage de feuilles - Google Patents

Dispositif de pliage de feuilles Download PDF

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Publication number
WO2015045142A1
WO2015045142A1 PCT/JP2013/076502 JP2013076502W WO2015045142A1 WO 2015045142 A1 WO2015045142 A1 WO 2015045142A1 JP 2013076502 W JP2013076502 W JP 2013076502W WO 2015045142 A1 WO2015045142 A1 WO 2015045142A1
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WO
WIPO (PCT)
Prior art keywords
sheet
pad
pressing
unit
folding
Prior art date
Application number
PCT/JP2013/076502
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English (en)
Japanese (ja)
Inventor
勉 石井
荒井恵一
Original Assignee
株式会社太陽技研
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 株式会社太陽技研 filed Critical 株式会社太陽技研
Priority to US14/917,117 priority Critical patent/US20160207733A1/en
Priority to CN201380079963.9A priority patent/CN105593151A/zh
Priority to JP2015538775A priority patent/JP6010701B2/ja
Priority to EP13894132.3A priority patent/EP3028975A1/fr
Priority to PCT/JP2013/076502 priority patent/WO2015045142A1/fr
Publication of WO2015045142A1 publication Critical patent/WO2015045142A1/fr

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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
    • B65H45/00—Folding thin material
    • B65H45/12—Folding articles or webs with application of pressure to define or form crease lines
    • B65H45/14—Buckling folders
    • B65H45/142—Pocket-type folders
    • B65H45/144—Pockets or stops therefor

Definitions

  • the present invention relates to a sheet folding apparatus provided with a sheet speed reducing means for temporarily stopping or slowing down a sheet such as printing paper on a transfer path.
  • a sheet folding apparatus a sheet transporting unit that feeds and transports sheets stacked on a sheet stacking unit one by one, a sheet stopper that prevents the progress of the sheet transported by the sheet transporting unit, and a sheet stopper And a sheet bending means that bends with the bent portion of the sheet partially blocked by being prevented (Patent Document 1).
  • Patent Document 2 discloses that a restraining member including rubber is rotatably attached to a predetermined shaft, and the restraining member is pressed against paper by a solenoid and stopped. However, in this method, since the entire rubber surface is in close contact with the paper, the paper moves with the restraining member, and the paper is wrinkled. With this, a stable folding position cannot be secured.
  • Patent Documents 3 and 4 disclose that a sheet is stopped by pressing a clamp from vertically above. However, in this method, the sheet is strongly pressed, so that the sheet may be damaged.
  • An object of the present invention is to solve the above-described problems and provide an apparatus that can accurately fold a sheet at a predetermined position while reducing damage to a sheet such as paper.
  • the present invention includes sheet transfer means 11, 12, 13, and 14 for transferring a sheet S along a predetermined path, and sheet speed reduction means 6a and 6b for reducing at least a part of the sheet being transferred by the sheet transfer means.
  • a sheet folding apparatus comprising: folding means 11, 13, 11 and 14 for bending the portion of the sheet bent by being decelerated by the sheet decelerating means; and a control unit for controlling the sheet decelerating means.
  • the seat deceleration means is A guide member 62 for receiving the sheet being transferred by the sheet transfer means; A plate-shaped pressing member 63 having a predetermined thickness, and a pressing member mounting portion 66 provided with the pressing member on an end surface facing the sheet and rotatably held by a predetermined fulcrum 63.
  • a restraining member that presses the sheet traveling along the guide member against the guide member at an edge ED1 of the pressing member;
  • a deterring member drive unit 65 that rotates the deterring member around the fulcrum,
  • the restraining member includes a standby position where the pressing member is not in contact with the sheet, and a pressing position where the edge of the pressing member is in contact with the sheet, but the entire surface of the pressing member is not in contact with the sheet.
  • the restraining member moves from the standby position to the pressing position by rotating in the same direction as the traveling direction of the sheet, and from the pressing position to the standby position by rotating in the direction opposite to the traveling direction of the sheet.
  • the inhibition member driving unit rotates the inhibition member from the standby position to the pressing position in accordance with a command from the control unit,
  • the restraining member is held so as to rotate about an axis parallel to the traveling direction of the sheet,
  • the restraining member is rotated by a reaction when the sheet is pressed against the guide member by an edge of the pressing member.
  • FIG. 1 is a perspective view of a sheet folding apparatus according to an embodiment of the present invention. It is a figure which shows the state which pulled out the auxiliary guide member of the sheet folding apparatus which concerns on embodiment of this invention. It is a perspective view of an auxiliary guide member concerning an embodiment of the invention. It is operation
  • FIG. 1 It is a block diagram of the control system of the seat speed reduction means which concerns on embodiment of this invention. It is explanatory drawing (timing chart) of the seat speed reduction means which concerns on embodiment of this invention. It is explanatory drawing of the correction table which concerns on embodiment of this invention. It is explanatory drawing of the drive time setting table which concerns on embodiment of this invention. It is a flowchart of the sensor selection process which concerns on embodiment of this invention. It is operation
  • FIG. 1 is a perspective view of a sheet folding apparatus according to an embodiment of the present invention.
  • the sheet folding apparatus 1 includes a sheet stocker 2 that is inclined downward toward the inside of the apparatus 1, a discharge tray 80 positioned below the sheet stocker 2, and an operation panel PAN for specifying how to fold a sheet (paper).
  • a discharge tray 80 is an exit E of the sheet.
  • the back surface of the sheet folding apparatus 1 can be removed.
  • This back surface is an auxiliary guide member 90 that receives a sheet protruding from sheet deceleration means 6a and 6b, which will be described later, on the curved inner surface.
  • the inner surface of the auxiliary guide member 90 is as shown in FIG.
  • a plurality of (9) plates are provided along the traveling direction of the sheet. All of these plates have the same shape, and the shape thereof is roughly cut out in a half oval shape (half egg shape). The corner generally forms a quarter arc.
  • the auxiliary guide member 90 receives a sheet protruding from the sheet speed-reducing means 6 a and 6 b at the cross section of the plate provided on the inner surface thereof.
  • the sheet decelerating means 6a and 6b can be made smaller than the sheet, so that the sheet folding apparatus 1 can be reduced in size.
  • the sheet stocker 2 is a portion for storing a foldable sheet S (a regular sheet in this example) in a stacked state.
  • a slat plate 3 made of rubber or the like is provided on the one end portion on the lower side in the tilt direction.
  • the sheets S stacked on the sheet stocker 2 are rolled up by the scooping plate 3 and fed out one by one from the upper sheet S in order.
  • a sliding plate 4 is provided for guiding the sheet S that has passed over the facing plate 3.
  • a separating plate 5 made of rubber or the like.
  • there is a known air suction type As the supply means, a friction type, an air suction type or other means can be adopted.
  • 10 is a supply roller that is provided above the scooping plates 3 and 5 and is in rolling contact with the upper surface of the sheet S passing through the scooping plates 3 and 5.
  • Numeral 11 is a driving roller located on the downstream side of the sheet S fed out between the separating plate 5 and the supply roller 10.
  • Numerals 15 and 16 are conveying rollers that transfer the sheet S that has passed between the driving roller 11 and the driven roller 14 to the outlet E (which communicates with the discharge tray 80).
  • the rollers 10 to 16 constitute sheet transfer means for transferring the sheet S along a predetermined path.
  • the driving roller 11 and the driven roller 13 are also bending means for bending the portion of the sheet bent by the sheet speed reducing means 6a.
  • the driving roller 11 and the driven roller 14 are also a bending unit that bends a portion of the sheet bent by the sheet speed reducing unit 6b.
  • Reference numeral 17 denotes a motor (sheet transfer means driving unit) that rotationally drives the supply roller 10, the driving roller 11, and the conveying roller 151.
  • the transmission unit 18 is a transmission unit for transmitting the power of the motor 17.
  • the transmission unit 18 includes a pulley 18a provided on the output shaft of the motor 17, a pulley 18b provided coaxially with the drive roller 11, a gear 18c provided coaxially with the supply roller 10, and externally meshed with the gear 18c.
  • the supply roller 10 is intermittently rotated by the action of a clutch (not shown) provided on the same axis.
  • a clutch not shown
  • the sheet S on the sheet stocker 2 can be fed out one by one at a predetermined timing by the supply roller 10 that rotates intermittently while continuously rotating the driving roller 11 and the driven rollers 12, 13, and 14.
  • the conveyance path 19 is a conveyance path for guiding the sheet that has passed between the driving roller 11 and the driven roller 14 to the outlet E.
  • the conveyance path 19 includes a pair of upper and lower plates 19a and 19b disposed in close proximity to each other in parallel.
  • the lower plate 19b is partially cut away to expose the outer peripheral portions of the transport rollers 15 and 16.
  • the sheet speed reducing units 6 a and 6 b are disposed obliquely upward and obliquely downward at positions facing the outer periphery of the drive roller 11.
  • the angle between the sheet deceleration means 6a and 6b is about 90 °.
  • the sheet decelerating means 6a and 6b temporarily decelerate the sheet S being transferred by the sheet transferring means so as to bend. Note that “deceleration” includes stopping the sheet S completely.
  • the upper sheet decelerating means 6 a decelerates the sheet S fed through between the driving roller 11 and the driven roller 12.
  • the lower sheet decelerating means 6 b decelerates the sheet S fed between the driving roller 11 and the driven roller 13.
  • FIG. 7 to 9 are explanatory views of the seat speed reducing means 6a and 6b. Since the seat speed-reducing means 6a and 6b are the same, the symbols “a” and “b” are omitted when it is not necessary to distinguish them in the following description.
  • the sheet speed reducing means 6 includes an upper guide plate 61 and a lower guide plate 62 that face each other in close proximity to each other via a gap G that allows the sheet S to enter.
  • the upper guide plate 61 and the lower guide plate 62 are formed by pressing a steel plate.
  • a gap G formed between the upper guide plate 61 and the lower guide plate 62 is, for example, about 1 to 3 mm.
  • the pad 63 is a rubber pad that presses the sheet S entering the gap G against the inner surface of the gap G (in this example, the upper surface of the lower guide plate 62) from the thickness direction.
  • the pad 63 is provided on the receiving end side where the sheet S of the gap G enters and exits.
  • the right side is the traveling direction of the sheet S. When the sheet S is bent, the sheet S returns from the traveling direction to the opposite side.
  • FIG. 64 is a pad moving means for moving the pad 63 between a predetermined standby position and a pressing position.
  • FIG. 7 shows the standby position of the pad 63. The standby position and the pressing position will be described in detail later.
  • the pad moving means 64 includes a solenoid 65 installed on the upper guide plate 61 as a drive source, a pad fixing bar 66 with the pad 63 attached to the bottom surface, and a transmission link that transmits the expansion / contraction driving force of the solenoid 65 to the pad fixing bar 66. 67.
  • the pad fixing bar 66 extends along the upper guide plate 61 in a direction perpendicular to the sheet entrance direction with respect to the gap G.
  • the extending direction of the pad fixing bar 66 is parallel to the end of the sheet S.
  • a bracket 66 a is attached to the center of the pad fixing bar 66.
  • a pair of left and right brackets 66 b are also attached to both ends in the longitudinal direction of the pad fixing bar 66.
  • the hatching applied to the portion of the pad fixing bar 66 clearly indicates the pad fixing bar 66 and does not represent a cross section.
  • the upper guide plate 61 is formed with a long hole 61a formed by cutting out an arrangement portion of the pad fixing bar 66, and brackets 61b and 61b formed by bending both end portions of the long hole 61a.
  • the brackets 61b and 61b and the brackets 66b and 66b are connected by pivots 68 and 68, respectively.
  • the telescopic rod 65 a of the solenoid 65 and the bracket 66 a are connected by a transmission link 67.
  • the solenoid 65 is driven to extend and contract, the pad fixing bar 66 rotates about the pivot 68 (performs an arc motion). Thereby, the pad 63 moves between the standby position and the pressing position.
  • the bracket 61b can be a metal block or the like instead of cutting and raising.
  • a coil spring 69 is provided on the telescopic rod 65a. Due to the elasticity of the spring, when the solenoid 65 is not driven, the pad 63 is in the standby position. When the solenoid 65 is driven, the elasticity of the spring 69 is overcome and the telescopic rod 65a contracts, and the pad 63 moves to the pressing position. When there is no drive current, the solenoid 65 moves the pad 63 to the standby position by the expansion rod 65a extending due to the elasticity of the spring 69.
  • the upper guide plate 61 is provided with a sheet entry sensor 7.
  • the sensor 7 detects the end of the sheet that enters the gap G.
  • the sheet approach sensor 7 is, for example, a reflective photoelectric switch.
  • the pad 63 pressing member
  • the pad fixing bar 66 pressing member mounting portion
  • the thickness of the pad 63 is a in FIG.
  • a pad 63 is provided on the end surface (lower surface) closer to the sheet S of the pad fixing bar 66.
  • the pad fixing bar 66 is rotatably held at a fulcrum FC.
  • the fulcrum FC corresponds to the pivot 68.
  • AP is the operating point of the driving force of the solenoid 65, and F is the acting force.
  • the restraining members 63 and 66 are in the standby position. That is, the pad 63 is not in contact with the sheet S.
  • Reference numeral 61c in FIG. 10 denotes a restraining member stopper for retaining the restraining members 63 and 66 at the standby position.
  • an angle formed by a line perpendicular to the surface of the pad 63 and the traveling direction of the sheet S is about 55 °.
  • the solenoid 65 is driven, and the restraining members 63 and 66 are moved as indicated by dotted lines and are in the pressed position. That is, the sheet S is pressed against the inner surface of the lower guide plate 62 by the edge ED1 of the pad 63.
  • the display of the lower guide plate 62 is omitted.
  • the edge ED1 is the one farther from the entry position of the sheet S out of the two edges of the pad 63 existing along the traveling direction of the sheet S.
  • the edge ED1 contacts the sheet S because the sum of the thickness a of the pad 63 and the length c from the end surface (lower surface) of the pad fixing bar 66 contacting the sheet S to the fulcrum FC is the distance h from the fulcrum FC to the sheet S. It is because it is slightly smaller than.
  • an angle formed by a line perpendicular to the surface of the pad 63 and the traveling direction of the sheet S is about 76 °.
  • the difference in angle between the standby position and the pressing position is about 20 °.
  • the restraining members 63 and 66 move from the standby position to the pressing position by rotating about 20 ° in the same direction as the traveling direction of the sheet S, and are pressed by rotating about 20 ° in the direction opposite to the traveling direction of the sheet S. Return from position to standby position.
  • the length b of the pad 63 is shorter than the length d of the end face of the pad fixing bar 66.
  • the pad 63 is provided close to the end of the pad fixing bar 66 on the entry side of the sheet S. For this reason, the edge (edge of the pressing member mounting portion) ED ⁇ b> 2 on the side opposite to the entry side of the sheet S on the end surface of the pad 63 is not covered with the pad 63. Accordingly, the restraining members 63 and 66 in FIGS. 10 and 11A and 11B have two edges ED1 and ED2.
  • the edge ED1 contacts the sheet S at the pressing position as shown in FIG. 11B, but the edge ED2 Therefore, the thickness a of the pad 63 should be selected so as not to contact the sheet S.
  • the pad 63 Since the pad 63 is configured to move in an arc and the brake is applied to the sheet S at its edge ED1, the sheet S can be firmly held, and the sheet S is thick and slows down sufficiently even when moving fast. Can be made.
  • the pad 63 In addition to the driving force of the solenoid 65, the pad 63 is pulled in the traveling direction of the sheet S by the frictional force generated between the sheets S, whereby the pad 63 further moves in an arc. As a result, the pad 63 is more strongly pressed against the seat S, so that a larger braking force can be obtained.
  • the brake at the edge ED1 it is possible to effectively decelerate using the traveling force of the seat S.
  • the angle formed by the line perpendicular to the surface of the pad 63 and the traveling direction of the sheet S is made smaller than 90 °, so that the sheet S can be sufficiently decelerated and a stable folding position can be obtained. Can be secured. If the angle becomes 90 ° and the entire surface of the pad 63 comes into contact with the sheet S, a stable folding position cannot be secured. If the angle exceeds 90 °, the sheet S cannot be stopped. Contrary to the above (1), the brake is weakened by the traveling force of the seat S.
  • FIG. 11C shows an example in which the length b of the pad 63 is the same as the length d of the end face of the pad fixing bar 66.
  • the edge ED2 does not exist.
  • the embodiment shown in FIG. 11C does not achieve the effect (2), but provides the effects (1) and (3).
  • CONT is a control unit that controls the solenoids 65a and 65b and the motor 17 based on signals from the operation panel PAN and a plurality of sensors.
  • the control unit CONT includes a CPU, a ROM, a RAM, and an I / O. Control is performed by the CPU executing a program stored in the ROM.
  • a signal for instructing how to fold the sheet S is performed.
  • a signal for instructing how to fold the sheet S is performed.
  • how to fold refer to FIG. 20 and the description thereof.
  • the sensors connected to the control unit CONT are as follows.
  • the sheet size sensor SS detects the size of the sheet S placed on the sheet stocker 2.
  • the detected sizes are A4, A3, and the like. Since the sheet size sensor SS is known, a detailed description thereof will be omitted. Note that the size of the sheet S may be input from the operation panel PAN instead of the sheet size sensor SS. In some cases, it is not necessary to provide the sheet size sensor SS.
  • the paper feed sensor FS is a sensor for detecting that the sheet S has been taken into the sheet transfer means 10-16.
  • the paper feed sensor FS is, for example, an optical sensor (such as a photo interrupter), and is provided, for example, in the vicinity of the straw plate 3 or the supply roller 10.
  • the sheet entry sensors 7a and 7b are sensors that detect the entry of the sheet S to the sheet deceleration units 6a and 6b. An example of the installation position is shown in FIG.
  • the paper discharge sensor ES is a sensor that detects the discharge of the folded sheet S.
  • the paper discharge sensor ES is provided at the exit E.
  • the rotary encoder RE is a sensor that detects the amount of rotation of the drive roller 11.
  • the rotary shaft of the rotary encoder RE is connected to the rotary shaft of the drive roller 11 directly or through a transmission mechanism such as a gear.
  • the rotary encoder RE outputs a pulse according to the rotation angle. For example, each time the driving roller 11 rotates ⁇ , one pulse is output.
  • the rotation angle of the drive roller 11 can be known by counting the pulses. Further, the movement amount of the sheet S can be known based on the number of pulses.
  • FIG. 14 shows a control system for the seat speed reduction means 6a or a control system for the seat speed reduction means 6b. Since the control contents of both are almost the same, in the following description, “a” and “b” are not described, and the seat speed reducing units 6a and 6b are not distinguished.
  • the control system in FIG. 14 is realized by the CPU executing a program.
  • the control system is also realized by hardware such as an IC.
  • Reference numeral 100 denotes a predetermined time (T1 in FIG. 15, the number of pulses PN1, and correction described later) from the timing (t0 in FIG. 15) at which the sheet entrance sensor 7 detects the entrance of the sheet S (the end of the sheet S).
  • This is a solenoid-on signal generator that controls to start driving the solenoid 65 at the timing (t1 in FIG. 15) after the subsequent number of pulses PN1 ′).
  • a solenoid drive time setting unit that sets the time (T2 in FIG. 15) during which the solenoid 65 is driven, and controls to stop the drive of the solenoid 65 at the timing (t2 in FIG. 15) when this time has elapsed. It is.
  • the 102 is a speed calculation unit that calculates the drive speed of the motor 17 based on the drive information (for example, current value) of the motor 17. For example, when the drive current is I0, I1, and I2, it can be known in advance that the drive speed is v0, v1, and v2. Therefore, the speed is calculated using this.
  • the drive information for example, current value
  • SW is a switch for turning on and off the current flowing from the power source PS to the solenoid 65.
  • the switch SW is turned on by the output of the solenoid-on signal generation unit 100 and turned off by the output of the solenoid drive time setting unit 101.
  • the solenoid-on signal generation unit 100 sets the drive start timing of the solenoid (suppression member drive unit) 65 that drives the suppression members 63 and 66 based on the instruction of how to fold the sheet S from the operation panel PAN and the output of the sheet size sensor SS.
  • Comparator 1003 that outputs an ON signal to switch SW when compared with the output of setting unit 1001 and a correction that stores an adjustment time determined in accordance with the driving speed of motor (sheet transfer means driving unit) 17 Part (correction table) 1004.
  • the solenoid-on position setting unit 1001 determines the folding position based on the folding method (two-fold, three-fold, etc.) and the size of the sheet S (A3, A4, etc.). Since the procedure for determining the folding position is known, the description thereof is omitted.
  • the folding position which is the output of the solenoid-on position setting unit 1001, is expressed by the number of output pulses PN1 of the rotary encoder RE (or the corrected pulse number PN1 'if corrected).
  • the counter counts the number of output pulses after t0.
  • the comparator 1003 turns on the solenoid 65 when the counted number of pulses reaches PN1 (or PN1 ').
  • the period T1 corresponds to the time required for the rotary encoder RE to output PN1 (or PN1 ′) pulses.
  • the position of the sheet S to which the restraining members 63 and 66 are to be braked (corresponding to PN1 or PN1 ') does not change, but the period T1 changes depending on the rotational speed of the motor 17. It can also be seen that the solenoid-on position setting unit 1001 sets the solenoid 65 on timing corresponding to the folding position.
  • the correction unit (correction table) 1004 performs correction to remove the influence of ⁇ T.
  • the correction table shown in FIG. 16 is provided, and the value of PN1 is corrected according to the driving speed of the motor 17 to obtain PN1 ′.
  • PN1 ' PN1- ⁇ 1. This corresponds to the actual period from sheet detection to sheet suppression when PN1 'performs correction.
  • This correction may be performed by the solenoid-on position setting unit 1001. Alternatively, it is added to the output of the counter 1002. The same applies to ⁇ 2 and ⁇ 3.
  • the folding position (number of pulses PN1) does not change depending on the driving speed of the motor 17, but the number of pulses generated at the time delay ⁇ T changes, so the correction unit 1004 is necessary.
  • the correction unit 1004 can also be regarded as adjusting the ON timing of the solenoid 65 using the adjustment values ⁇ 1, ⁇ 2, and ⁇ 3.
  • the adjustment value is determined based on the time ⁇ T required to move from the standby position to the pressing position.
  • the absolute value of the adjustment value increases as the driving speed of the motor 17 increases. In other words, as the driving speed of the motor 17 increases, t1 approaches t0 by correction.
  • the delay at the first speed is ⁇ T1
  • the number of pulses output by the rotary encoder RE at ⁇ T1 corresponds to the adjustment value (correction value) ⁇ 1.
  • the solenoid drive time setting unit 101 has a table as shown in FIG. According to the figure, when the sheet S is the first size and the driving speed of the motor 17 is the first speed, the on-time T2 of the solenoid 65 is ⁇ 11.
  • the restraining members 63 and 66 are for decelerating the sheet S, bending the sheet S, and bending the bent portions by the bending means (the driving roller 11 and the driven roller 13). In order to achieve this purpose, the restraining members 63 and 66 must slow down the sheet S sufficiently.
  • the time required for the deceleration is a function of the size (mass) of the sheet S and its traveling speed. Since the kinetic energy of the sheet S is proportional to the mass and proportional to the square of the traveling speed, the driving time ⁇ of the table in FIG. 17 becomes longer as the transfer speed of the sheet S increases as described above. The larger the length, the longer.
  • the driving time ⁇ is desirably long enough to bend the sheet S to the extent that the above-described purpose is achieved, and short enough not to prevent the sheet S from moving to the bending means.
  • the solenoid-on signal generator 100 sets the drive start timing based on the output of the sheet feed sensor FS instead of the sheet entry sensor 7. This processing flowchart is shown in FIG.
  • T1 in FIG. 15 is shorter than or equal to the time delay ⁇ T.
  • T1 can be made sufficiently long, so that the restraining members 63 and 66 can be brought into contact with appropriate positions.
  • the threshold value is determined based on the relationship between T1 and ⁇ T, for example. For example, when the correction result by the correction unit 1004 becomes 0 or smaller than a predetermined value (a value that allows a margin for improving reliability), the output of the paper feed sensor FS is used.
  • a predetermined value a value that allows a margin for improving reliability
  • FIG. 19 shows that the pad 63 of each of the seat speed reducing means 6a and 6b is in the pressing position, but in actuality, either the standby position or the pressing position according to the situation of the action as follows. It is in.
  • the sheet S is first fed into the gap G of the sheet speed reducer 6a positioned between the driving roller 11 and the driven roller 12 and positioned above.
  • the pad 63 is in the standby position and allows the sheet S to enter the gap G.
  • the solenoid 65 is driven based on the detection signal, thereby moving the pad 63 to the pressing position.
  • the sheet S is pressed against the inner surface of the gap G by the pad 63.
  • the sheet S is sandwiched between the pad 63 and the lower guide plate 62 and is prevented from proceeding.
  • the rear end side of the sheet S is between the driving roller 11 and the driven roller 12, and continues to be sent forward (downstream) from both the rollers 11 and 12.
  • the sheet S bends downward between the driving roller 11 and the pad 63.
  • the bent portion Sa is caught between the driving roller 11 and the driven roller 13.
  • the bending portion Sa of the sheet S is bent by the driving roller 11 and the driven roller 13, and the sheet S is fed into the gap G of the sheet speed reduction unit 6b positioned below with the bent portion as a leading end.
  • the sheet S is bent in the same manner as the sheet decelerating means 6 a, and the bent portion Sb is wound between the driving roller 11 and the driven roller 14.
  • the sheet S that has passed between the driving roller 11 and the driven roller 14 is discharged to the outside through the conveyance path 19.
  • FIG. 20A shows the outer three-fold
  • FIG. 20B shows the inner three-fold
  • FIG. 20C shows the four-fold.
  • a shutter device (not shown) is provided in the vicinity of one of the sheet speed reducing means 6a and 6b, and the shutter device prohibits the sheet S from entering the gap G, and the other sheet speed reducing means only allows the sheet S to be moved. By decelerating, the sheet S can be folded in half as shown in FIG.
  • the folding method in FIG. 20 depends on the operation timing of the pad 63.
  • the operation timing is set by the solenoid-on signal generator 100.
  • the pad 63 and its moving means 64 may be provided on the bottom surface side of the lower guide plate 62 so that the sheet S that has entered the gap G is pressed against the lower surface (inner surface) of the upper guide plate 61 by the pad 63.
  • the pair of upper and lower guide members forming the gap G is not limited to a plate material such as the upper guide plate 61 and the lower guide plate 62.
  • the guide member may be configured by stacking a plurality of bar members in parallel.
  • the pivots 68 and 68 of the pad fixing bar 66 are rotatably held by the brackets 61b and 61b of the upper guide plate 61, respectively. Since the brackets 61 b and 61 b are integrally formed with the upper guide plate 61, the pad fixing bar 66 does not move except that it rotates around the pivots 68 and 68, and the upper and lower guide plates 61 and 62 are not moved. The positional relationship is constant. That is, the position of the pad fixing bar 66 was fixed. This is also true for the relationship with the sheet S passing between them.
  • the pad fixing bar 66 may be attached to the upper guide plate 61 and the lower guide plate 62 in exactly parallel. However, a slight error occurs due to the work accuracy. Further, the above condition is not satisfied even when the pad 63 is worn unevenly due to long-term use. If the above conditions are not satisfied even a little, the above disadvantageous phenomenon occurs. For example, even if the difference between the distance from the pivot 68 at one end of the pad fixing bar 66 to the lower guide plate 62 and the distance from the pivot 68 at the other end to the lower guide plate 62 is about 0.5 mm, the above disadvantageous phenomenon occurs. It will occur.
  • 21 to 24 show the speed reduction means 6 having a mechanism that satisfies the above-described conditions and can suppress the occurrence of the inconvenient phenomenon. According to the decelerating means 6, the contact between the pad 63 and the sheet S is performed simultaneously and to the same extent in the longitudinal direction.
  • FIG. 21 is a plan view of the speed reduction means 6 according to a modification
  • FIG. 22 is a front view thereof
  • FIG. 23 is a right side view thereof
  • FIG. 24 is an exploded view.
  • CA is a fulcrum of the seesaw (rotating axis of the pad fixing bar 66).
  • the pad fixing bar holding portion 161 is a pad fixing bar holding portion attached to a seesaw mechanism attaching portion 61V configured by bending an end portion of the upper guide plate 61 at a right angle.
  • the pad fixing bar holding portion 161 is provided with shaft holes 161h for receiving the pivots 68, and includes side surfaces 161b and 161b provided in parallel with each other, and a base portion 161c facing the seesaw mechanism attaching portion 61V while supporting them.
  • the pad fixing bar holding portion 161 is formed by bending a plate-like member.
  • the pad fixing bar holding part 161 is attached to the seesaw mechanism attaching part 61V by two screws (not shown). These screws are fixed to the mounting plate 162 via the collars C2 and C2, respectively.
  • the holes (not shown) in the bases 161c through which the collars C2 and C2 pass are slightly larger than the collars C2 and C2, so that the pad fixing bar holding part 161 is located with respect to the seesaw mechanism attaching part 61V. Can move a little.
  • a hole (shown but not labeled) that is large enough to allow the transmission link 67 and the telescopic rod 65a to pass through is provided at approximately the center of the base 161c and the seesaw mechanism mounting portion 61V. .
  • the collar 163 is fitted into this hole of the seesaw mechanism mounting portion 61V through this hole of the base portion 161c.
  • the collar 163 does not come off because it is pressed by the mounting plate 162.
  • the collar 163 is also provided with a hole large enough to allow the transmission link 67 and the telescopic rod 65a to pass therethrough.
  • the pad fixing bar holding part 161 can be rotated by the collar 163.
  • the center of rotation is the transmission link 67 and the telescopic rod 65a, that is, the drive shaft of the solenoid 65.
  • the pad fixing bar 66 is supported at a predetermined point (for example, the center) as a fulcrum CA, and can move around the fulcrum CA.
  • the rotation axis is an axis parallel to the traveling direction of the sheet S.
  • the rotation shaft is the drive shaft of the solenoid 65.
  • a very small range of rotation is sufficient. For example, it is about 0.5 mm at the end of the pad fixing bar 66.
  • friction applying means 164 and 164 are provided outside the collars C2 and C2.
  • the friction applying means 164 includes a screw 164a, a coil spring 164b, and a washer 164c.
  • the seesaw mechanism mounting portion 61V is provided with a hole (not shown but not shown) that is larger than the screw 164a, through which the screw 164a passes through the screw hole of the base portion 161c (shown but not shown). Not fixed).
  • the friction applying means 164 does not block the movement of the pad fixing bar holding part 161, but makes the pad fixing bar holding part 161 difficult to move due to the frictional force generated between the washer 164c and the seesaw mechanism attaching part 61V. This frictional force can be adjusted by turning the screw 164a.
  • the friction applying means 164 is for preventing the pad fixing bar 66 from moving freely.
  • the solenoid 65 is driven by the friction applying means 164 so that the pad 63 comes into contact with the sheet S, a predetermined load F is applied to the sheet S, and the pad fixing bar 66 is rotated only when this reaction exceeds the frictional force. become.
  • the minimum force required to move the pad fixing bar 66 is set as a threshold value Fth.
  • the threshold value Fth corresponds to the frictional force and can be adjusted with the screw 164a.
  • the friction applying means 164 may be provided on the side surface 161b.
  • the friction applying means 164 may apply friction to the collar 163.
  • one or a plurality of brake shoes contacting the side surface of the collar 163 can be provided, and the contact pressure can be adjusted.
  • the friction applying unit 164 may be a unit that directly contacts sponge or resin with the pad fixing bar holding portion 161.
  • the friction applying means 164 may use not only a mechanical force but also an electromagnetic force.
  • a permanent magnet / electromagnet is provided in the pad fixing bar holding portion 161
  • an electromagnet / permanent magnet is provided in the upper guide plate 61 or the lower guide plate 62
  • the pad fixing bar 66 is utilized by utilizing the attraction / repulsion force therebetween. It adjusts the ease of movement.
  • FIG. 25 is an explanatory diagram of the operation of the above example.
  • This figure is a front view of the pad fixing bar 66 as seen from the direction in which the sheet S enters. The movement of the pad fixing bar 66 as seen from the side is the same as in FIG.
  • CA is the rotation axis / fulcrum. In this example, it is a drive shaft of the solenoid 65.
  • the pad fixing bar 66 moves like a seesaw with CA as a fulcrum. Thereby, the space
  • the pad fixing bar 66 moves when a load F equal to or greater than the threshold Fth is applied by the action of the friction applying means 164. Even if the operator carelessly touches the pad fixing bar 66 or the pad fixing bar holding portion 161 when the cover is opened for maintenance and exposed to the speed reduction means 6, if the force at this time is smaller than the threshold value Fth It doesn't move.
  • the threshold value Fth is, for example, 1000 gf to 1500 gf. If the threshold value Fth is too small, the degree of skewing varies. If the threshold value Fth is too large, it takes time to complete the seesaw operation, and many sheets S are consumed until the above condition is satisfied. .
  • the threshold value Fth is preferably determined so as to satisfy the condition that the skew feeding can be suppressed and the number of sheets until the seesaw operation is completed is equal to or less than a predetermined number.
  • the load F applied from the pad 63 to the sheet S is not constant mainly due to the speed, weight, and weight of the sheet S. It is considered that most of the force that causes the sheet S to stand still is a force that is generated when the pad 63 receives the traveling force of the sheet S itself (the same action as the wedge). This force varies with time.
  • the strength of the solenoid 65 and the load F are not so related. The role of the solenoid 65 is to bring the pad 63 and the sheet S into close contact with each other, and the sheet S is not stationary only by the force of the solenoid 65.
  • the threshold value Fth may be set so as to satisfy the above condition at the slowest speed, and therefore at the speed with the smallest load F (lowest speed). If the seesaw mechanism operates even when the load is small, the seesaw mechanism operates properly even when the load is large, and the contact between the pad 63 and the sheet S is performed simultaneously and to the same extent in the longitudinal direction. As the load F increases, the skew reduction effect by the seesaw mechanism increases. Therefore, if the skew reduction effect is achieved at the lowest speed, the skew reduction effect can be achieved at other speeds.
  • FIG. 26 shows the actual measurement results of the speed reduction means 6 shown in FIGS.
  • the figure shows the measurement results of the case where the left end of the pad fixing bar 66 of the upper sheet speed reducing means 6a is raised by 0.5 mm and the case where the right end is raised by 0.5 mm when viewed from the front.
  • this 0.5 mm is an offset amount, and the state where the distance between the pad 63 and the sheet S is the same at all locations is 0 mm.
  • the horizontal axis in FIG. 26 indicates the number of folding times (the number of sheets).
  • the figure shows a case where 20 sheets S are folded.
  • the vertical axis indicates the degree of skew (unit: mm). This corresponds to x in FIG.
  • the solid line in FIG. 27 indicates the sheet S in which no skew is generated, and the dotted line indicates the sheet S in which the skew is generated.
  • the right side is positive and the left side is negative with respect to the traveling direction of the sheet S.
  • the skew of the fifth and subsequent sheets is stable at 0.5 mm or less.
  • the contact between the pad 63 and the sheet S is automatically adjusted so that the contact between the pad 63 and the sheet S is performed simultaneously and at the same level in the longitudinal direction of the pad 63. Skew does not occur, or even if it occurs, the sheet folding quality does not deteriorate.
  • 21 to 24 can absorb dimensional errors and aging that occur in the manufacturing process, and can provide sheet folding with excellent quality.

Landscapes

  • Folding Of Thin Sheet-Like Materials, Special Discharging Devices, And Others (AREA)

Abstract

La présente invention concerne un dispositif de pillage de feuilles comprenant un moyen de réduction de vitesse permettant d'arrêter une feuille en appuyant sur celle-ci. Un élément de pression tel qu'un caoutchouc forme le moyen de réduction de vitesse sur l'extrémité distale d'un élément de tige qui est maintenu rotatif. La vitesse de la feuille est réduite du fait que l'élément de pression appuie sur la feuille selon un certain angle. Il est possible d'éviter que des plis apparaissent sur le papier, car la surface du caoutchouc n'est pas entièrement en contact avec le papier. En outre, l'élément de pression est soutenu par un mécanisme à bascule. Le caoutchouc est en contact uniforme avec la feuille au moyen du mécanisme à bascule et la qualité du pliage est améliorée.
PCT/JP2013/076502 2013-09-30 2013-09-30 Dispositif de pliage de feuilles WO2015045142A1 (fr)

Priority Applications (5)

Application Number Priority Date Filing Date Title
US14/917,117 US20160207733A1 (en) 2013-09-30 2013-09-30 Sheet folding device
CN201380079963.9A CN105593151A (zh) 2013-09-30 2013-09-30 片材折叠装置
JP2015538775A JP6010701B2 (ja) 2013-09-30 2013-09-30 シート折り装置
EP13894132.3A EP3028975A1 (fr) 2013-09-30 2013-09-30 Dispositif de pliage de feuilles
PCT/JP2013/076502 WO2015045142A1 (fr) 2013-09-30 2013-09-30 Dispositif de pliage de feuilles

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2013/076502 WO2015045142A1 (fr) 2013-09-30 2013-09-30 Dispositif de pliage de feuilles

Publications (1)

Publication Number Publication Date
WO2015045142A1 true WO2015045142A1 (fr) 2015-04-02

Family

ID=52742341

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Application Number Title Priority Date Filing Date
PCT/JP2013/076502 WO2015045142A1 (fr) 2013-09-30 2013-09-30 Dispositif de pliage de feuilles

Country Status (5)

Country Link
US (1) US20160207733A1 (fr)
EP (1) EP3028975A1 (fr)
JP (1) JP6010701B2 (fr)
CN (1) CN105593151A (fr)
WO (1) WO2015045142A1 (fr)

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3797820A (en) 1971-03-22 1974-03-19 Broadbent & Sons Ltd Thomas Self-centering crossfolder
JPS6023253A (ja) 1983-07-20 1985-02-05 Fuji Xerox Co Ltd 紙折り装置
JPS6341377A (ja) 1986-07-11 1988-02-22 ア−ル・フアンク・アンド・カンパニ−・インコ−ポレ−テツド 材料シ−トの折りたたみのための方法及び装置
JPH05238637A (ja) 1992-02-24 1993-09-17 Duplo Corp 紙折り機
JPH11106127A (ja) * 1997-10-03 1999-04-20 Minolta Co Ltd 紙折り装置
JP2006347692A (ja) * 2005-06-15 2006-12-28 Nisca Corp シート束搬送装置及びこれを用いた製本装置
WO2013005296A1 (fr) * 2011-07-05 2013-01-10 株式会社太陽技研 Dispositif d'arrêt de feuille et dispositif de pliage de feuille

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3874652A (en) * 1972-05-08 1975-04-01 Decision Consultants Apparatus for feeding sheet material from the bottom of a stack
US6663551B2 (en) * 2001-10-26 2003-12-16 Pitney Bowes Inc. Buckle chute folding machine with a deflector control mechanism
JP5680795B2 (ja) * 2012-04-24 2015-03-04 株式会社太陽技研 シート折り装置

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3797820A (en) 1971-03-22 1974-03-19 Broadbent & Sons Ltd Thomas Self-centering crossfolder
JPS6023253A (ja) 1983-07-20 1985-02-05 Fuji Xerox Co Ltd 紙折り装置
JPS6341377A (ja) 1986-07-11 1988-02-22 ア−ル・フアンク・アンド・カンパニ−・インコ−ポレ−テツド 材料シ−トの折りたたみのための方法及び装置
JPH05238637A (ja) 1992-02-24 1993-09-17 Duplo Corp 紙折り機
JPH11106127A (ja) * 1997-10-03 1999-04-20 Minolta Co Ltd 紙折り装置
JP2006347692A (ja) * 2005-06-15 2006-12-28 Nisca Corp シート束搬送装置及びこれを用いた製本装置
WO2013005296A1 (fr) * 2011-07-05 2013-01-10 株式会社太陽技研 Dispositif d'arrêt de feuille et dispositif de pliage de feuille

Also Published As

Publication number Publication date
US20160207733A1 (en) 2016-07-21
JP6010701B2 (ja) 2016-10-19
JPWO2015045142A1 (ja) 2017-03-02
EP3028975A1 (fr) 2016-06-08
CN105593151A (zh) 2016-05-18

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