JP5183180B2 - Drilling device - Google Patents

Description

  The present invention relates to a punching device that punches holes in a sheet conveyed from an image forming apparatus such as a copying machine, a printing machine, and a printer, and relates to an improvement of a punching mechanism that prevents noise during punching.

  Generally, a punching device that punches filing punch holes in a sheet of paper or the like is used as an office machine by manually pressing a punch member on several sheets and punching a sheet from a printing machine, a copier, or the like Those that drill automatically are known. The former is widely known as a device in which a cylindrical punch member is disposed on a frame member so as to be movable up and down with a sheet interposed therebetween, and is pushed down by an operation lever to penetrate the sheet. On the other hand, the latter is used by being incorporated in various devices as a device for setting a sequentially conveyed sheet at a predetermined processing position and pressing a punch member with a driving motor to make a hole. In these apparatuses, the sheet is simultaneously punched at two, three or four places at a predetermined interval, and the number and interval of these holes are set to a unified standard.

  Therefore, conventionally, for example, the structure disclosed in Patent Document 1 is known as the latter apparatus. In this document, an upper frame and a lower frame set with a sheet sandwiched between them are arranged at a predetermined interval, and a plurality of punch members are supported on the upper frame so as to be movable up and down. Receiving hole) is formed. An apparatus is disclosed in which a plurality of punch members are actuated in a perforating direction by a drive motor to perforate a predetermined position of a sheet. Therefore, a plurality of punch members are selectively operated according to the standard, for example, a 2-hole punch, a 3-hole punch, etc., and the selected plurality of punch members are operated with a slight delay in time, whereby the drive motor The load torque is reduced.

  For this reason, the plurality of punch members are connected to a drive motor via cam means. In Patent Document 1, a follower pin provided on each punch member is engaged with a slide cam having an inverted V-shaped cam groove, and this slide cam is supported so as to be movable along the upper frame. The pinion of the drive motor is connected to the rack gear formed integrally. The eccentric cam of each punch member selectively punches the sheet according to the rotation angle of the drive shaft, and similarly, the punching timing is varied by giving a time difference to the operation of the plurality of punch members selected.

The punch member in the device of Patent Document 1 receives a thrust force in the punching direction from the V-shaped cam and punches the sheet in the process of moving from the top dead center to the bottom dead center in the thrust direction without rotating in the radial direction. A structure is disclosed.
JP 2001-9791 A (FIGS. 6 to 8)

  As described above, when a plurality of punch members are selectively operated in the drilling direction by the cam means, conventionally, a groove cam is provided on a transmission member (sliding cam member) that reciprocates in a linear direction as in, for example, Patent Document 1 described above. A cam follower member (hereinafter referred to as “cam pin”) integrally formed with the punch member is fitted into the groove cam. The groove cam is configured in a V-groove shape (see FIG. 11) so that the cam pin moves up and down along the groove cam by connecting the transmission member to a drive motor and reciprocating linearly.

  Further, similarly to the above-described conventional apparatus, a cylindrical cam having a V-shaped groove cam is provided on the punch member side, and a cam pin that engages with the groove cam is fixed to the base frame. When this cylindrical cam (punch member) is connected to a drive motor and rotated, the punch member moves up and down along the groove cam while rotating in the radial direction. Thus, by punching the punch member in the radial direction while rotating the punch member in the radial direction to form punch holes in the paper sheet, it becomes possible to punch the paper sheet at a high speed with a low load (light load). . The present applicant filed a patent application as Japanese Patent Application No. 2007-060841 for a perforated structure using this cylindrical cam.

  However, when the punch member is caused to perform a punching operation from the top dead center to the bottom dead center with the cam groove and the cam pin as described above, the following noise problem occurs. That is, unless the cam groove and the cam pin are fitted so as to have a small clearance (clearance) d, smooth movement cannot be obtained. Therefore, for example, when a slide cam having a V-groove-shaped cam surface is driven to reciprocate at high speed, or when a cylindrical cam is driven to rotate at high speed, the cam pin collides with the cam surface of the cam groove to generate noise (impact sound). Explaining this according to the operation state diagram of the slide cam shown in FIG. 11, the slide cam 90 is moved to the left side of the drawing. At this time, the punch member 91 is located at the top dead center in the state of FIG. 5A, starts moving to the bottom dead center side in the state of FIG. 5B, and immediately before the bottom dead center in the state of FIG. It reaches the bottom dead center in the state (d). During this operation, a clearance d exists between the cam groove 92 and the cam pin 93. The clearance d is set to an optimum value at which the cam surface 92a and the cam pin 93 move smoothly. Usually, the clearance d varies (machine difference) due to parts accuracy and wear during use.

  Therefore, when the slide cam 90 is moved to the left side of the figure at a high speed, the cam pin 93 collides with the cam surface 92a of the cam groove 92 at a position where the punch member 91 is displaced from the top dead center side to the bottom dead center side in FIG. An impact sound is generated by this collision, and the cam pin 93 vibrates violently. Thereafter, the cam pin 93 moves in the direction of the bottom dead center while vibrating within the range of the clearance d (the state shown in FIG. 3C). At this time, the cam pin 93 has a difference in the body of the clearance d. Reach the bottom dead center with repeated collisions. At this bottom dead center position, the cam pin 93 has a machine difference at that position within the clearance d.

  Thus, the cam pin 93 moving along the cam groove 92 collides with the cam surface 92a in (b) and generates an impact sound. In (c), the cam pin 93 vibrates between the cam surfaces at an unstable speed. Heading to the bottom dead center and reaching the bottom dead center in (d) above, the lowest position varies depending on the machine difference of the clearance d.

  Therefore, in the cam mechanism in which the cam pin moves from the top dead center to the bottom dead center along the conventional groove cam, the impact noise of the cam pin becomes a problem as device noise during high speed driving. In particular, when a plurality of punch members, for example, four holes are simultaneously drilled, the noise is transmitted to the user as abnormal noise. In addition, if there is a clearance between the pin and the cam surface at the bottom dead center position, the cutting edge position of the punch member reaching the lowest end is different, so that reliable punching may not be obtained depending on the sheet material to be punched. In other words, when the paper is thin, the blade edge may be inserted into the sheet more than necessary (overrun phenomenon), and when the paper is thick, the blade edge may not completely penetrate the sheet (incomplete punching).

  Therefore, the present inventor configures the upper cam surface and the lower cam surface that form the cam groove to be relatively movable (gap adjustment is possible), and elastically biases one of the upper and lower cam surfaces. The inventor has come up with the idea that the above-described noise problem and the variation of the bottom dead center position can be solved.

The main object of the present invention is to increase the speed and silence of the punching operation by the punch member when punch holes are formed in the paper sheet.
Furthermore, when the punch member is moved in the punching direction while rotating the punch member in the radial direction to punch the paper sheet, the speeding up and the noise reduction of the punch member are problems.

  In order to achieve the first object, the present invention provides cam means for perforating and moving a punch member supported on an appropriate base frame so as to move up and down between a top dead center and a bottom dead center. Is constituted by a cam groove and a cam follower member engaged with the cam groove. The cam surface of the cam groove and the cam follower member are configured to be able to move relative to each other, and a spring means is provided on one of the cam surface and the follower member so as to slide in pressure contact with each other. As a result, when the follower member collides with the cam surface, the sound is silenced by the action of the elastic force to suppress the apparatus noise. When the follower member is located at the bottom dead center, the cam surface is pressed by the elastic force, and the position is a punching operation. There is no misalignment each time.

  In order to achieve the second problem, a cylindrical cam having a cam groove is provided in the punch member, and the punch member is configured to rotate by a driving means. Then, the follower member engaged with the cam surface of the punch member is fixed to the base frame. As a result, the punch member moves up and down in the drilling direction while rotating in the radial direction. Therefore, the cam surface and the follower member are configured as described above. As a result, punch holes can be punched in the paper sheet at high speed and with a small torque, and at the same time, the noise reduction is achieved.

A punch member having a piercing blade at the tip, to transmit the punch member and the base frame for reciprocably supported in puncture hole direction, driving means for driving the punch member, the driving of the drive means to the punch member comprising a transmission member, and a cam means for converting the movement of the transmission member in the piercing movement of the punch member.
The cam means comprises: a cylindrical cam having a cam groove inclined at a predetermined angle in the drilling direction; a cam follower member that engages with the cam groove; and a spring means that imparts elastic force in the drilling direction to the cylindrical cam. The cylindrical cam is divided into an upper cam member and a lower cam member vertically in the drilling direction, and an upper cam surface formed on the upper cam member and a lower cam surface formed on the lower cam member are connected to the cam follower member. The elastic member is configured to be movable in the perforating direction at a small interval formed between the upper cam member and the lower cam member .

  The cam means is constituted by a cylindrical cam integrally attached to the punch member, and the cam groove is configured to be movable in the perforating direction with a small clearance, and the spring means is attached to the cylindrical cam. It arrange | positions so that the elastic force of a drilling direction may be provided.

  The cylindrical cam includes an upper cam member and a lower cam member attached to the punch member, and the cam groove includes an upper cam surface formed on the upper cam member and a lower cam formed on the lower cam member. The spring means is constituted by a leaf spring that presses the upper cam member and the lower cam member together.

  The transmission member is configured to apply a rotational force that rotates in a radial direction perpendicular to the punching direction to the punch member, and the cam means includes a cam groove that converts the rotational motion of the punch member into the punching motion. The cylindrical cam and a cam follower member attached to the base frame are configured to punch the paper while rotating the paper sheet.

  The transmission member is composed of a slide member that reciprocates in a predetermined direction, and the cam means is composed of a cam groove formed on one side and a cam follower member formed on the other side between the slide member and the punch member. .

  The present invention provides cam means for punching a punch member supported on a base frame so as to move up and down between a top dead center and a bottom dead center, and the cam means is a cam groove and a cam follower member engaged with the cam groove. The cam groove and the cam follower member can be moved relative to each other, and a spring means is provided on one of the cam surface and the follower member so as to slide in pressure contact with each other. Therefore, the following effects are produced.

  The cam surface forming the cam groove and the follower member (hereinafter referred to as “cam pin”) fitted to the cam groove are configured to move relative to each other and to be elastically engaged by the spring means. Therefore, even when the cam groove or the cam pin is moved at high speed, the impact when the two collide is alleviated by the elastic force of the spring means, and the impact sound is suppressed. Therefore, even if the cam member that moves the punch member up and down is moved at a high speed, it is possible to suppress the apparatus noise due to this, and it is possible to achieve high speed and low noise of the drilling operation. In particular, there is a significant reduction in noise in an apparatus configuration in which a plurality of punch members are arranged to simultaneously punch punch holes such as 2 holes, 3 holes, and 4 holes.

  In the present invention, the punch member is provided with a cylindrical cam having a cam groove, the punch member is rotated by driving means, and the follower member engaged with the cam surface is fixed to the base frame. It moves up and down in the drilling direction while rotating in the radial direction. In this way, by performing the punching operation while rotating the punch member, it is possible to reduce the driving torque and increase the speed of the punching operation. It is possible to reduce the noise generated in this case, and the present invention can simultaneously achieve high speed and low noise of the punching operation by the punch member.

  The present invention will be described in detail below based on the preferred embodiments shown in the drawings. FIG. 1 is an explanatory view showing the overall configuration of a perforating apparatus according to the present invention, and FIG. 2 is a cross-sectional view of the main part thereof. FIG. 3A is a perspective view of the punch member, and FIG. 3B is an explanatory view of the shape of the inclined cam.

[Punching device]
First, a perforating apparatus A according to the present invention will be described. As shown in FIG. 1, the punching apparatus A includes a lower frame (die plate) 35 for setting the punched sheet S and an upper frame (base) disposed with a small gap Sd between the lower frame 35. Frame) 30, a punch member 40 attached to the upper frame 30, and a blade receiving hole 38 provided in the lower frame 35. The upper frame 30 has a driving means (a driving motor M described later) for moving the punch member 40 up and down (perforating direction), and a transmission member (a rack described later) for transmitting the driving of the driving motor M to the punch member 40. The gear 51) and cam means (cylindrical cam 44 to be described later) for converting the movement of the transmission member into the punching movement of the punch member 40. Each configuration will be explained in detail.

  The upper frame 30 and the lower frame 35 are formed in a length according to the width size of the perforated sheet S, and a predetermined number of punches are formed by punch members 40 provided on the upper frame 30 on the sheet conveyed on the lower frame. Create a hole. For this reason, the punch member 40 is formed in an ordinary cylindrical shape, and a perforating blade 41 is provided at the tip thereof. A plurality of punch members 40 are arranged on the upper frame 30 at intervals according to a predetermined standard (file hole standard) according to the apparatus specifications such as 2 holes, 3 holes, 4 holes, and the like. In the illustrated example, the first punch member 40a, the second punch member 40b, the third punch member 40c, and the fourth punch member 40d are arranged at four locations, and two holes and four punch holes are selectively punched in the sheet. It is like that.

[Configuration of punch member]
Since each of the punch members 40a to 40d has the same structure, one of them will be described below with reference to FIGS. The punch member 40 shown in FIG. 2 shows a case where a drilling operation that moves up and down between a top dead center and a bottom dead center is constituted by a cylindrical cam (cam means; hereinafter the same) 44. The illustrated punch member 40 includes a punch shaft 42 having a perforating blade 41 at the tip, and a cylindrical cam 44 attached integrally to the punch shaft 42.

  The punch shaft 42 is formed of a metal material such as carbon steel into a cylindrical shaft shape, and a drilling blade 41 is formed at the tip (the lower end in FIG. 3A). The shape of the perforating blade 41 is a hollow cylindrical shape, and the tip thereof is formed in a sharp oblique shape. The cylindrical cam 44 is formed of a cylindrical synthetic resin cylinder. The cylindrical cam 44 is formed with an inverted V-shaped cam groove 45 on the outer periphery thereof, and is fitted to a cam pin 33c described later. As shown in FIG. 4C, the cylindrical cam 44 is divided into an upper cam member 44A and a lower cam member 44B. The upper cam member 44A has an upper cam surface 45a, and the lower cam member 44B has a lower cam member 44B. A lower cam surface 45b is formed. The upper cam surface 45a and the lower cam surface 45b form an inverted V-shaped cam groove 45.

  The cam members 44A and 44B that form the inverted V-shaped cam groove 45 are divided into upper and lower parts in this way in either the upper cam surface 45a or the lower cam surface 45b that forms the cam groove 45 in the axial direction (see FIG. This is because it can be moved in the vertical direction. The upper and lower cam members 44A and 44B divided and formed in this way are fitted to the punch shaft 42 to form an inverted V-shaped cam groove 45 as follows. As shown in FIG. 4B, a hollow hole 44bx is formed at the center of the lower cam member 44B, the punch shaft 42 is inserted into the hollow hole 44bx, and both are integrally coupled by a rotation stop pin 44by. .

  On the other hand, the upper cam member 44A is also provided with a hollow hole 44ax, and the punch shaft 42 is inserted through the hollow hole 44ax. The upper cam member 44A is fitted along the punch shaft 42 so as to be movable up and down. That is, as shown in FIGS. 4B and 4C, the lower cam member 44B is provided with a fitting concave groove 44bu, and the fitting convex portion 44au of the upper cam member 44A is fitted into the fitting concave groove 44bu. Yes. Accordingly, the upper cam member 44A and the lower cam member 44B are fitted to the punch shaft 42, and one of them (the illustrated lower cam member 44B) is integrally fixed to the punch shaft 42, and the other (the illustrated one is the upper cam). A member 44A) is fitted and supported so as to be movable up and down along the punch shaft.

  The upper cam member 44A is provided with a spring means 47 that constantly urges downward along the punch shaft. The illustrated spring means 47 is formed of a disk-shaped leaf spring, and an intermediate hole 47x through which the punch shaft 42 is inserted is formed at the center thereof. The leaf spring 47 is inserted into the punch shaft 42 and fixed to the punch shaft 42 with an E ring 48b through a washer 48a. The lower surface of the leaf spring 47 always presses and urges the upper end surface 44az of the upper cam member 44A downward.

  A rotational force is applied to the above-described cylindrical cam 44 from a drive motor M, which will be described later, and the rotational motion is converted in the perforating direction by the cam groove 45. Therefore, a passive gear 46 is integrally formed on the outer periphery of the lower cam member 44B at a position different from the cam groove 45. A rack gear (transmission member) 51, which will be described later, is meshed with the passive gear 46, and the rack gear 51 is reciprocated by the drive motor M to move the punch member 40 up and down (about the drive mechanism). Will be described later).

  Next, the cam shape of the cam groove 45 will be described with reference to FIG. The punching apparatus A includes a total of four punch members, ie, a first punch member 40a and a fourth punch member 40d for punching two holes, and a second punch member 40b and a third punch member 40c for further punching four holes. The case where it comprises is shown. Therefore, the cylindrical cam 44 of each punch member 40a to 40d is provided with an inclined cam surface 45θ inclined by a predetermined angle (θ) with respect to the drilling direction (vertical direction in FIG. 3A), and the first and fourth cam grooves 45ak. , 45dk and the second and third cam grooves 45bk, 45ck have two inclined cam surfaces 45θ (see FIG. 3B). The inclined cam surfaces 45θ of the first and fourth cam grooves 45ak and 45dk and one inclined cam surface 45θ of the second and third cam grooves 45bk and 45ck are respectively at the same angular position (first angular position) of the cylindrical cam 44. 4 holes are formed in the perforated sheet S at the first angular position. The cylindrical cam 44 is configured to make two holes in the perforated sheet S at the second angular position.

  At the second angular position, the first and fourth cam grooves 45ak and 45dk are formed as linear grooves that are horizontal in the outer circumferential direction of the cylindrical cam 44. Accordingly, the first to fourth cam grooves 45ak to 45dk engaged with the cam pins 33c fixed to the upper frame 30 are arranged so that the first to fourth punch members 40a to 40d are formed on the punched sheet S at the first angular position. Holes are punched, and the second and third punch members 40b and 40c punch two holes in the punched sheet S at the second angular position.

  Further, the other inclined cam surfaces 45θ of the second and third cam grooves 45bk, 45ck are formed at the same angular position at an angular position (second angular position) different from the first angular position of the cylindrical cam 44. At the position, two holes are made in the sheet.

  The cylindrical cams 44 are attached to the upper frame 30 so as to have a phase difference by a predetermined angle, and the punching timings of the punch members 40a to 40d are made different when simultaneously punching. That is, as shown in FIG. 1, when four holes are formed, each punch member 40a to 40d has a time difference (cam groove) in the order of the first punch member 40a, the second punch member 40b, the third punch member 40c, and the fourth punch member 40d. The timing of drilling is shifted with the difference of the deviation. Similarly, when the two holes are formed, the second punch member 40b and the third punch member 40c are provided with a phase difference in this order.

[Operation of cylindrical cam]
The cylindrical cam (cam means) 44 configured as described above is configured so that one of the upper cam surface 45a and the lower cam surface 45b constituting the inverted V-shaped cam groove 45 moves vertically with a small span in the drilling direction. The spring means 47 is provided on the movable cam surface (the above-described upper cam surface 45a). A cam pin 33c is fitted between the upper cam surface 45a and the lower cam surface 45b, and the cam pin 33c is fixed to the apparatus frame (upper frame 30).

  Therefore, the rack gear 51 applies a rotational force to the passive gear 46 formed on the lower cam member 44B. For example, when the rack gear 51 moves to the left side in FIG. 5, the punch member 40 rotates counterclockwise in FIG. At this time, the cam pin 33c comes into contact with the lower cam surface 45b of the cam groove 45 at the position p2 displaced from the top dead center p1 to the bottom dead center side shown in FIG. Thereafter, the cam pin 33c is guided by the upper cam surface 45a along the lower cam surface 45b and moves in the direction of the bottom dead center (the state shown in FIGS. 6C and 6D). Then, it reaches the bottom dead center p4 (the state shown in FIG. 6E), slightly overruns from the bottom dead center p4, and stops at the stop position p5 (the state shown in FIG. 6F).

  The engagement relationship between the cam pin 33c and the cam groove 45 from the bottom dead center p4 to the stop position p5 is such that the cam pin 33c collides with the upper cam surface 45a as shown in FIG. At this time, the upper cam surface 45a escapes upward as indicated by a chain line in FIG. The impact sound is mitigated by the action of the spring means 47, and the apparatus noise is suppressed. Note that, at this stop position p5, the load at the bottom dead center p4 varies depending on the thickness or material of the sheet. For this reason, the punch member 40 must be vigorously lowered (hit) to the bottom dead center p4, and the punch member 40 necessarily stops at the stop position p5 slightly overrun from the bottom dead center p4. At this time, the cam pin 33c collides with the upper cam surface 45a, but the upper cam surface 45a escapes upward, so that the noise is reduced.

  After punching the sheet by the above operation, the drive motor M is rotated in the reverse direction to move the rack gear 51 to the right side in FIG. Then, the punch member 40 returns from the stop position p5 to the bottom dead center p4, and then returns to the top dead center side to the illustrated p3 position, the p2 position, and the top dead center p1. At this time, the punch member 40 first descends to the bottom dead center side, then reverses the direction and moves upward to the top dead center side. At this time, the punch member 40 is subjected to a load of direction change that reverses the motion in the direction of the bottom dead center to the motion in the direction of the top dead center, and a load that peels the blade edge of the punching blade 41 from the punched sheet. On the other hand, the driving force of the rack gear 51 acting on the punch member 40 is low torque because it is immediately after the motor is started. Therefore, the returning operation of the punch member 40 becomes slow, and there arises a problem that the timing for carrying out the punched sheet to the outside has to be delayed.

However, since the above-described leaf spring (spring means) 47 acts on the punch member 40 of the present invention, the spring force fb shown in FIG. 7B acts on the upper cam surface 45a, and the plate force is applied by this spring force fb. The spring (spring means) 47 bends as shown in FIG. The impact acting on the upper cam member 44A due to the bending of the spring is alleviated, and the impact sound is reduced. Simultaneously with the reduction of the impact sound, the spring force fb acts as a restoring force for displacing the punch member 40 to the top dead center (upward in the figure) immediately after that. Therefore, if the rack gear 51 is rotated reversely immediately after the punch member 40 stops at the stop position p5, the above-described problem of insufficient torque occurs. However, when the leaf spring (spring means) 47 is restored, a force in the direction indicated by the arrow acts on the punch member 40. As a result, the punch member 40 quickly moves from the bottom dead center p4 toward the top dead center and returns to the top dead center p1. As described above, the cam pin 33c and the upper cam surface 45a are configured to be closely engaged with each other by the elastic force of the leaf spring (spring means) 47 so as to alleviate the impact acting on the upper cam member 44A. At this time, a small gap is formed between the cam pin 33c and the lower cam surface 45b in the form shown in FIG. On the other hand, the cam pin 33c and the lower cam surface 45b may form a groove interval of the cam groove 45 so as to closely engage each other without forming a gap as shown in FIG. With this configuration, the impact can be further reduced and the impact sound can be reduced.

  Next, the frame structure will be described. As shown in FIG. 2, the upper frame 30 is composed of a channel member having a U-shaped cross section, and guide holes 31a and 32a are provided in an upper guide 31 and a lower guide 32 that face each other vertically. In the punch member 40, the upper shaft portion 42a is fitted and supported in the guide hole 31a, and the lower shaft portion 42b is supported in the guide hole 32a. Therefore, the punch member 40 is supported by the upper frame 30 so as to be slidable in the vertical direction (perforation direction) in FIG.

  The lower frame 35 is provided with a blade receiving hole 38 that fits the perforating blade 41. The lower frame 35 is formed as a unit with the upper frame 30 and the lower frame 35 by forming a small gap Sd in the upper frame 30 and attaching them integrally with a fixing screw 39. A cam follower member 33 that engages with the cam groove 45 is fixed to the upper frame 30. The illustrated cam follower member 33 includes a pedestal portion 33a, a guide shaft portion 33b, and a cam pin 33c, and is fitted into a mounting hole formed in the upper frame 30 so as to have a predetermined positional relationship with the guide holes 31a and 32a. The part 33a is fixed with a screw or the like. The guide shaft portion 33b guides a slide member 50 described later, and the cam pin 33c is configured in a pin shape that engages with the cam groove 45. Accordingly, the punch member 40 is supported by the upper frame 30 so as to be slidable up and down, and the cam groove 45 is engaged and held by the cam pin 33c provided thereon. The cam pin 33c constitutes a cam follower member.

  A passive gear 46 is integrally attached to the punch member 40. This passive gear 46 is connected to a drive motor M, which will be described later, via transmission means (rack gear 51). In the punch member 40 configured in this way, the punching blade 41 and the upper and lower shaft portions 42a and 42b are made of a material having good polishing properties such as SUS steel. In addition, it may be formed of iron-based metal or ceramic. The cylindrical cam 44 and the passive gear 46 are preferably molded from a synthetic resin such as POM (Duracon resin) from the viewpoint of workability and quietness, but the material is not particularly limited. The punching blade 41 of the punch member 40, the cylindrical cam 44, and the passive gear 46 are integrated. This integration is for these three members to rotate integrally, and is integrated by insert molding at the time of molding, or fixed with a fixing screw, an adhesive or the like.

  Next, a slide member 50 is incorporated in the upper frame 30 so as to be movable in the left-right direction in FIG. A rack gear 51 is formed on the slide member 50, and the rack gear 51 meshes with the passive gears 46 of the punch members 40 a to 40 d arranged in a plurality (four in the drawing) on the upper frame 30 as described above. It is supposed to be. The slide member 50 is guided so as to be slidable in the vertical direction between the guide shaft portion 33b of the cam follower member 33 and the lower guide 32, and is moved back and forth between the back surface of the upper frame 30 and each passive gear 46. Guided (see FIG. 2) and supported so as to be movable in the left-right direction in FIG. As a result, the passive gear 46 of each punch member 40a to 40d and the rack gear 51 of the slide member 50 are engaged with each other, and each punch member 40a to 40d has a predetermined angular relationship (a phase difference described later) according to the amount of movement of the slide member 50. ) Will be rotated respectively.

  A drive motor M is connected to the slide member 50 as follows. A drive motor M is attached to the upper frame 30 by a bracket 53, and its rotation shaft is connected to the drive gear G1 via a reduction gear. The drive gear G1 is meshed with the rack gear 51 of the slide member 50. Therefore, the slide member 50 moves in the left-right direction in FIG. 54 is an encoder provided on the rotating shaft of the motor, and Se is an encode sensor for detecting this. The slide member 50 is provided with a position sensor for detecting its position.

  In the apparatus configuration described above, the punching operation for punching 2 or 4 holes in the sheet S to be punched such as paper is performed as follows. The punching apparatus A is provided with a control means (not shown), for example, by a control CPU. The operation of this control CPU (control means) will be described based on the flowchart of FIG.

  When the apparatus power is turned on and the apparatus is started (St100), the control means receives a selection signal (St101) for determining whether to drill two holes or four holes, for example, from the post-processing apparatus. In response to this instruction signal, the control means moves the slide member 50 to the home position (start position) (St102). At this time, the control means causes the drive motor M to overrun a predetermined amount from the home position, and then reverses the rotation direction. Then, the slide member 50 is positioned at the home position without backlash. In this state, the control unit stops the drive motor M and waits for the conveyance set of the punched sheet S.

  Next, when the perforated sheet S is prepared at a predetermined set position, the control means rotates the drive motor M by the set end signal (St103) and moves the slide member 50 rightward in FIG. 1 (St104). When the slide member 50 moves in the right direction, the rack gear 51 formed integrally therewith rotates the passive gear 46 in the counterclockwise direction. Then, the punch member 40 moves in the drilling direction (thrust direction) while gradually rotating counterclockwise from the state of FIG. 5A to the state of FIG. 6F. In this process, four or two punch holes are punched in the punched sheet S (St105).

  Next, the control means determines whether or not the punching operation has been completed using the home position sensor (St106). At this time, for example, if the preset jam time has elapsed (St107) and the sensor does not detect the operation end position, it is determined that a jam has occurred, and the drive motor M is rotated reversely (St108). By the reverse rotation of the drive motor M, the slide member 50 and the punch member 40 return to the home position, and this is detected by the position sensor (St109). Therefore, a control means jam signal is issued to display “jam” on the control panel of the post-processing apparatus, for example. At the same time, the apparatus power is turned off (St110).

  When the slide member 50 and the punch member 40 do not move to the home position due to the reverse rotation of the drive motor M, it is regarded as a device failure and an error signal is issued, and “device failure” is displayed on the control panel (St111). When the punching of the sheet S is normally executed, the control unit issues a punching end signal to the post-processing apparatus C, for example, and the post-processing apparatus C carries the sheet S out of a predetermined set position. Before and after the sheet S is unloaded, the control means rotates the drive motor M in the reverse direction to return the slide member 50 to the home position HP. In this state, it waits for the next sheet to be prepared at the set position.

  In this process, according to the present invention, when the punch member 40 moves from the home position to the punching position, the punching blade 41 rotates in the radial direction simultaneously with the movement in the thrust direction, and FIGS. 5 (a), 5 (b), 5 (c) and FIG. Punch holes are punched in the punched sheet S by twisting motion in the order of 6 (d) (e) (f). For this reason, the shearing force exerted on the perforated sheet S by the perforating blade 41 increases several times as compared with the case where the perforating blade 41 is simply moved in the thrust direction. For example, in this embodiment, the shearing force can be increased by a factor of 2, and as a result, the load torque of the drive motor M can be halved. Conversely, even if the drilling speed is doubled, the load on the drive motor M does not increase, and the transmission mechanism can be simplified and the punching operation can be speeded up.

  Accordingly, as shown in FIGS. 5 and 6, as the slide member 50 having the rack gear 51 moves, the punch member 40 rotates counterclockwise from the top dead center p <b> 1 along the inclined cam surface 45 </ b> θ while the punching start point. Move to p2, touch the sheet and start drilling. Then, while rotating in the same direction, the sheet passes through the sheet, moves to the punching end point p3, and then moves to the bottom dead center p4. Next, when the slide member 50 further moves, the punch member 40 moves (rises) from the bottom dead center p4 to the top dead center p1. At this time, the punch member 40 returns to the punching end point p3 while rotating counterclockwise along the inclined cam surface 45θ, further returns to the punching start point p2, and finally returns to the top dead center p1.

  Next, since the slide member 50 moves in the opposite direction when the next sheet is punched, the punch member 40 repeats the same operation while rotating clockwise. That is, at the time of punching odd-numbered sheets sequentially punched, the punch member 40 moves from top dead center p1 to bottom dead center p4 while rotating clockwise, for example, and then top dead center from bottom dead center p4 while rotating in the same direction. Move to point p1. When punching even-numbered sheets, the punch member 40 moves and returns from the top dead center p1 to the bottom dead center p4 and from the bottom dead center p4 to the top dead center p1 while rotating in the reverse direction and clockwise. .

  Therefore, even if the scrap paper piece 80 is clogged at the tip of the punching blade 41, it is shaken off by the rotation at the time of punching or is shaken off by the rotation in the opposite direction at the time of punching the next sheet. In this way, the scrap paper piece 80 adhering to the perforating blade 41 receives the rotational force in the forward and reverse directions, is separated from the blade edge by centrifugal force, and is distributed roughly in all directions to the waste box 81 disposed at the lower part of the lower frame 35. Accumulated and stored.

  An electrostatic drum 10 is provided in the printing unit 3, and a print head 9, a developing device 11, a transfer charger 12, and the like are disposed around the drum 10. The print head 9 is composed of, for example, a laser light emitter, and forms an electrostatic latent image on the electrostatic drum 10. A toner ink is attached to the latent image by the developing device 11 and printed on a sheet by the transfer charger 12. . This print sheet is fixed by the fixing device 13 and carried out to the paper discharge path 17. The paper discharge unit 4 is provided with a paper discharge port 14 and a paper discharge roller 15 formed in the casing 1. Reference numeral 16 denotes a circulation path. The print sheet from the paper discharge path 17 is turned upside down on the switchback path and then sent to the registration roller 7 again to form an image on the back surface of the print sheet. In this way, the print sheet on which one side or both sides are formed is carried out from the paper discharge port 14 by the paper discharge roller 15.

  In the figure, reference numeral 20 denotes a scanner unit which optically reads a document image to be printed by the print head 9. As is generally known, the platen 23 on which a document sheet is placed and set, a carriage 21 that scans a document image along the platen 23, and an optical device that photoelectrically converts an optical image from the carriage 21. It comprises a reading means (for example, a CCD device) 22. In the illustrated example, a document feeder 25 for automatically feeding a document sheet to the platen is provided on the platen 23.

  Therefore, a post-processing device C is connected to the paper discharge port 14 of the image forming apparatus B. The post-processing apparatus C includes a sheet conveyance path 26, a punch unit 27 and a paper discharge stacker 28 disposed in the conveyance path 26. The sheet conveying path 26 is provided with an aligning means 26a on the upstream side of the punch unit 27, and aligns the sheet trailing edge. Further, a forward / reverse roller 26b is disposed in the transport path 26, and a sheet from the carry-in entrance 26c is abutted and aligned with the aligning means 26a. At the same time, the forward / reverse roller 26b carries the sheet from the punch unit 27 to the paper discharge stacker 28. . Si shown in the figure is a sheet detection sensor. The punch unit 27 is composed of the apparatus shown in FIG.

  The post-processing apparatus C configured as described above receives the printed sheet from the image forming apparatus B from the carry-in entrance 26c, detects the sheet rear end by the sheet detection sensor Si, and the timing at which the sheet rear end passes through the aligning unit 26a. Thus, the forward / reverse rotation roller 26b is reversely rotated (counterclockwise in the figure). Then, the sheet is switched back and the rear end of the sheet is abutted and aligned with the aligning means 26a. After this alignment, the forward / reverse roller 26b stops and holds the sheet in that position. In this state, the punch unit 27 drives the drive motor M to execute the above-described punching operation. After execution of the punching operation, the forward / reverse rotation roller 26b is rotated in the clockwise direction in the figure by the end signal from the position sensor Sp1, and the punched sheet is carried out to the paper discharge stacker 28. In addition, although not shown, a staple unit, a stamp unit, and the like are incorporated in the post-processing apparatus C according to apparatus specifications.

  As described above, the cylindrical cam 44 has been described when the punch member is moved up and down in the present invention, but the present invention can also be applied to the conventional cam mechanism described based on FIG. This case will be described with reference to FIG. 10, the same structure as that of FIG. 11 described above is denoted by the same reference numeral, and the description thereof is omitted. As described with reference to FIG. 11, the slide cam 90 is connected to the drive motor and is configured to reciprocate with a predetermined stroke. The slide cam 90 is provided with a plurality of inverted V-shaped cam grooves 92. A cam pin 93 formed integrally with a punch member 91 (not shown) is fitted in the cam groove 92. These configurations are not shown in FIG. 10 but are the same as those described in FIG.

  Therefore, the cam groove 92 formed in the slide cam 90 includes an upper cam surface 92a integrated with the slide cam 90 and a movable lower cam surface 92b. The lower cam surface 92b is formed on a bracket 96 supported by a support shaft 95 so as to be movable up and down on the slide cam 90. A spring 97 urges the lower cam surface 92b upward on the bracket 96 at all times. Therefore, when the slide cam 90 is vigorously moved in the direction of arrow a in the figure, when the cam pin 93 collides with the bottom dead center position of the inverted V-shaped cam, the lower cam surface 92b moves downward by the action of the spring 97, and the impact To ease. At the same time, when the slide cam 90 is reversely moved in the opposite direction, the upward return of the punch member is assisted by the accumulated force stored in the spring 97. Therefore, the same action as that of the leaf spring 47 provided on the cylindrical cam 44 is achieved.

BRIEF DESCRIPTION OF THE DRAWINGS Explanatory drawing which shows the whole structure of the punching apparatus concerning this invention. FIG. 2 is a cross-sectional view of a main part in the apparatus of FIG. It is explanatory drawing of the punch member in the apparatus of FIG. 1, (a) is the perspective view, (b) is shape explanatory drawing of an inclination cam. (A) thru | or (d) The assembly block diagram of a punch member. (A) thru | or (c) The operation state explanatory drawing which shows the piercing | piercing state in the apparatus of FIG. (D) thru | or (f) The operation state explanatory drawing which shows the piercing | piercing state in the apparatus of FIG. It is explanatory drawing of the punch member in the apparatus of FIG. 1, (a) shows the engagement relationship of the cam pin and cam groove in a stop position, (b) is explanatory drawing of the action state of a spring force. The flowchart which shows operation | movement of the control means in the apparatus of FIG. (A) It is explanatory drawing which shows the whole structure of the image forming apparatus concerning this invention, and a post-processing apparatus, (b) The principal part enlarged view of a post-processing apparatus. The principal part explanatory drawing which shows the drive mechanism of the punch member different from the apparatus of FIG. Explanatory drawing which shows the drive mechanism of the conventional punch member.

Explanation of symbols

A Drilling device 30 Upper frame (base frame)
31 Upper guide 32 Lower guide 33c Cam pin 35 Lower frame (die plate)
38 Blade receiving hole 40 Punch member 40a First punch member 40b Second punch member 40c Third punch member 40d Fourth punch member 41 Drilling blade 42 Punch shaft 42a Upper shaft portion 42b Lower shaft portion 44 Cylindrical cam (cam means)
44A Upper cam member 44ax Hollow hole 44au Fitting convex portion 44az Upper end surface 44B Lower cam member 44bu Fitting concave portion 44bx Hollow hole 44by Rotation stop pin 45 Cam groove 45a Upper cam surface 45ak First cam groove 45b Lower cam surface 45bk Second cam Groove 45ck Third cam groove 45dk Fourth cam groove 45θ Inclined cam surface 46 Passive gear 47 Spring means 47x Middle hole 48a Washer 48b E-ring 50 Slide member 51 Rack gear (transmission member)

Claims (3)

A punch member having a perforated blade at the tip;
A base frame for reciprocably supporting said punch member into puncture hole direction,
Driving means for driving the punch member,
A transmission member for transmitting driving of the drive means to the punch member,
A cam means for converting the movement of the transmission member in the piercing movement of the punch member,
With
The cam means is
A cylindrical cam integrally attached to the punch member and having a cam groove inclined at a predetermined angle in the drilling direction;
A cam follower member engaged with the cam groove;
Spring means for applying elastic force in the drilling direction to the cylindrical cam;
Consisting of
The cylindrical cam is
It is divided into an upper cam member and a lower cam member vertically in the drilling direction,
The upper cam surface formed on the upper cam member and the lower cam surface formed on the lower cam member are configured to be movable in the drilling direction at a small gap formed between the cam follower member,
A perforating apparatus in which an elastic force in a direction in which the upper cam member and the lower cam member are pressed against each other is applied by the spring means . The cylindrical cam is integrally attached to the punch member,
2. The perforating apparatus according to claim 1, wherein the spring means is a leaf spring . The transmission member is configured to impart rotational force to the punch member,
The cam means is composed of the cylindrical cam having a cam groove for converting the rotational movement of the punch member into the drilling direction movement, and a cam follower member attached to the base frame,
The punch member perforating apparatus according to claim 1 or 2, characterized in that drilling while rotating the paper sheet.

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