JP2018116217A - Drive transmission mechanism, sheet processing apparatus, and image forming apparatus - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a drive transmission mechanism that is excellent in operation responsiveness during connection and separation and can improve a degree of freedom in arrangement of a pendulum gear, and a sheet processing apparatus, and an image forming apparatus.SOLUTION: A drive transmission mechanism comprises: a gear holder that is rotatably supported coaxially with a rotation shaft of a sun gear; and a pendulum gear that is rotatably supported by the gear holder and revolves while rotating meshed with the sun gear, where the pendulum gear is separated from a driven gear according to a direction of rotation of the sun gear. The drive transmission mechanism includes a counter moment member that, when a moment centered on the rotation shaft of the sun gear generated by a self weight including the gear holder and the pendulum gear is a self-weight moment, generates a counter moment acting on an opposite direction to the self-weight moment centered on the rotation shaft of the sun gear.SELECTED DRAWING: Figure 5

Description

  The present invention relates to a drive transmission mechanism used for transmitting a drive to a sheet conveying roller such as an image forming apparatus, and more particularly to a drive transmission mechanism, a sheet processing apparatus, and an image forming apparatus provided with a pendulum gear.

A clutch mechanism using a general pendulum clutch or a one-way clutch is known as a drive transmission mechanism used in a conventional drive system for this type of sheet conveying roller. In this case, when pulling out the sheet to the downstream side of the roller in the jam processing, the jam handling force can be reduced because the pendulum clutch and the one-way clutch act on the idling side. However, when pulling out upstream, the pendulum clutch and the one-way clutch act on the drive transmission side, so that there is a case where the jam handling force becomes large and it is difficult to handle the jam due to the sheet being broken. Moreover, a large-scale and poorly responsive separation system such as a solenoid is necessary for releasing the drive.
On the other hand, a drive transmission mechanism using a pendulum gear as described in Patent Document 1 has been proposed. The pendulum gear is provided so as to be able to swing around the rotation shaft of the reduction gear while maintaining meshing with the reduction gear (sun gear). When the motor rotates forward, the pendulum gear engages with the conveyance roller drive gear, The driving force is transmitted to. On the other hand, at the time of reverse rotation of the motor, the pendulum gear is separated from the transport roller driving gear. Therefore, if the motor is rotated in reverse during jamming, the pendulum gear is separated from the conveyance roller drive gear, so that the jammed sheet can be pulled out lightly in both the upstream and downstream directions of the conveyance roller. It becomes.

JP 2011-90040 A

However, even in a system that employs a pendulum gear, if the weight of the pendulum gear is large, the operation responsiveness at the time of connection and separation deteriorates. In order not to reduce the operation responsiveness, it can be used only for a pendulum gear having a small self-weight moment, and the degree of freedom of arrangement of the pendulum gear is limited.
An object of the present invention is to provide a drive transmission mechanism, a sheet processing apparatus, and an image forming apparatus that are excellent in operation response at the time of connection and separation and can increase the degree of freedom of arrangement of the pendulum gear.

In order to achieve the above object, the present invention provides:
A sun gear to which the driving force from the driving source is transmitted;
A gear holder rotatably supported coaxially with the rotating shaft of the sun gear;
A pendulum gear that is rotatably supported by the gear holder and revolves while rotating in mesh with the sun gear,
In the drive transmission mechanism configured such that the pendulum gear is separated from the driven gear according to the rotation direction of the sun gear,
If the moment about the rotation axis of the sun gear generated by its own weight including the gear holder and the pendulum gear is defined as the self-weight moment, it is opposite to the self-weight moment about the rotation axis of the sun gear with respect to the gear holder. A counter moment member that generates a counter moment acting in a direction is provided.
In addition, a sheet processing apparatus of the present invention includes the drive transmission mechanism.
An image forming apparatus according to the present invention includes the drive transmission mechanism.

  According to the present invention, since the self-weight moment including the gear holder and the pendulum gear is canceled by the counter moment member, the operation response at the time of connection and separation is excellent, and the degree of freedom of arrangement of the pendulum gear can be increased.

1 is a schematic view of an image forming apparatus equipped with a sheet post-processing apparatus according to Embodiment 1 of the present invention. FIG. 2 is a perspective view of a lower transport unit and a gear box of the paper post-processing apparatus of FIG. 1. The figure which shows the drive transmission part of the conveyance roller of FIG. 2, and a roller drive gear. The perspective view and exploded view which show the structure of the gear train in the gear box of FIG. Explanatory drawing which shows the operation state of the gear train of FIG. The perspective view which shows the structure of the gear train of the drive transmission mechanism which concerns on Embodiment 2 of this invention.

Hereinafter, the present invention will be described in detail based on illustrated embodiments. However, the dimensions, materials, shapes, relative arrangements, and the like of the component parts described in this embodiment are not intended to limit the scope of the present invention only to them.
[Embodiment 1]
FIG. 1 is a schematic cross-sectional view illustrating an example of an image forming apparatus 1 including a sheet post-processing device 19 as a sheet processing device in which a drive transmission device according to Embodiment 1 of the present invention is incorporated. The sheet post-treatment 19 may be configured to be connected to the image forming apparatus 1 as an option, or may be configured integrally as a part of the image forming apparatus 1.
In this image forming apparatus 1, a sheet P (sheet) stacked on a sheet feeding unit 2 is pressed against a photosensitive drum 3 a and a transfer roller 4 of a process cartridge 3 by a sheet feeding roller 2 a provided in the sheet feeding unit 2. It is fed toward the transfer nip. The paper P includes not only paper but also films and the like.
In the process cartridge 3, a toner image is formed on the sightseeing drum 3a by a known electrophotographic process. That is, an electrostatic latent image is formed on the surface of the photosensitive drum 3 a charged by the charging roller 3 b by a light beam from an exposure device (not shown), a toner image is formed by the developing roller 3 c, and the toner image is transferred to the transfer roller 4. Is transferred onto the paper P.
The sheet P on which the toner image has been transferred is conveyed to the fixing device 6 and is nipped and conveyed at the nip portion between the fixing sleeve 7a and the pressure roller 7b, and the toner image is applied to the sheet P by applying predetermined heat and pressure. Heat fixing. The fixing sleeve 7a includes a heater 7c, and the fixing sleeve 7a and the heater 7c are pressed against the pressure roller 7b by a pressure spring (not shown). The fixing device 6 further includes a pressure system and a thermistor (not shown), and the temperature is adjusted by a controller (not shown) according to the type of paper, the environment such as temperature and humidity, and the toner amount.
The paper P on which the toner image has been fixed by the fixing device 6 is conveyed further downstream by the fixing paper discharge roller pair 8.
A switching flapper 9 is provided downstream of the fixing paper discharge roller pair 8, and includes a paper conveyance path, a paper discharge path from the main body paper discharge roller pair 10 to the paper discharge tray 11, and a path to the paper post-processing device 19. And switched to.
The sheet post-processing device 19 has an upper discharge tray 16 and a lower discharge tray 18 which are two discharge trays, and the discharge port is switched by a discharge bin switching flapper 13. That is, the sheet is discharged to the lower sheet discharge tray 18 through the lower sheet discharge roller pair 17, and is discharged to the upper sheet discharge tray 16 by the upper sheet discharge roller pair 15 via the conveying roller pairs 12 and 14. The roller pairs 8, 10, 12, 14, 15, and 17 are not particularly designated in FIG. 1, but a pair of rollers on the driving side and the driven side are pressed against each other, and a sheet is placed on the pressing portion. It is configured to be sandwiched and conveyed.
When a paper jam occurs in the apparatus, after the main body jam processing door 5 is released, the fixing device 6 is removed from the image forming apparatus 1 to process the paper jam. Further, when a paper jam occurs in the paper post-processing device 19, the paper jam can be handled by releasing the upper jam handling door 20. Further, the paper that has been jammed between the image forming apparatus 1 and the paper post-processing device 19 while being sandwiched between the conveying roller pair 12 is sent from either the main jam processing door 5 or the upper jam processing door 20. Jam processing can be performed.

Next, the lower transport unit 21 will be described with reference to FIG.
In addition to the transport roller 12 shown in FIG. 2, the lower transport unit 21 includes a lower paper discharge roller pair 17, a lower paper discharge tray 18, a paper discharge bin switching flapper 13 and a transport guide for connecting them as shown in FIG. Consists of. The conveying roller pair 12 includes a driving side roller 12a and a driven side roller 12b pressed against the driving side roller 12a. A roller driving gear 23 is fixed to a shaft end portion of the driving side roller 12a. The roller drive gear 23 is disposed outside a bearing (not shown) that supports the conveyance roller 12, that is, outside the side frame of the lower conveyance unit 21. The roller driving gear 23 drives the driving side roller 12a of the conveying roller pair 12, and the driven side roller 12b rotates.
A gear box 50 is disposed at a position adjacent to the roller drive gear 23. In the gear box 50, a plurality of gears described later are supported by the frame 24 and the gear support plate 20, and the output gear 22 as a pendulum gear is exposed at a position facing the roller drive gear 23. When the output gear 22 and the roller driving gear 23 mesh with each other, the driving force is transmitted to the conveying roller 12. Further, the lower transport unit 21 is inserted into the main body frame 24 from the C direction (the direction opposite to the paper discharge direction) in the drawing, and is fastened to the frame 24 by screws (not shown).

Next, with reference to FIG. 3, power transmission from the conveying roller pair 12 to the lower paper discharge roller pair 17 will be described. FIG. 3 is a cross-sectional view taken along the line DD in FIG. 2, and in order to simplify the description, the description of the components other than the components to be described is omitted.
The output gear 22 includes a gear portion 23a in which teeth are formed, and a cylindrical portion 22b having no teeth provided coaxially with the gear portion 22a. The roller drive gear 23 fixed to the conveying roller 12 also includes a gear part 23a having teeth and a cylindrical part 23b without teeth provided coaxially with the gear part. The gear part 23a is an output gear. The gears 22a are engaged with each other to transmit drive. On the other hand, the cylindrical part 23b plays the role of guaranteeing the center-to-center distance between the gear part 22a and the gear part 23a by abutting against the cylindrical part 22b of the output gear 22.
The driving force received by the roller driving gear 23 is transmitted to the lower discharge roller pair 17 via the timing belt 27. The timing belt 27 is wound around a pulley 25 fixed to the driving roller 12 a of the conveying roller pair 12 and a pulley 26 connected to the driving roller 17 a of the lower paper discharge roller pair 17. The pulley 26 of the lower paper discharge roller 17 is positioned by a stopper 28. The ratio of the number of teeth of the pulley 25 and the pulley 26 is set to be approximately the same as the diameter ratio of the driving rollers 12a and 17a connected to the pair of conveying rollers 12 and the pair of lower paper discharge rollers 17, respectively.

Next, with reference to FIGS. 4A and 4B, a gear train inside the gear box 50 constituting the drive transmission mechanism of the present invention will be described. In order to simplify the description, the gear support plate 20 is not displayed.
As shown in FIG. 4A, the gear train includes a sun gear 33 to which a driving force from a motor M as a driving source is transmitted, a carrier 34 as a gear holder, and an output as a pendulum gear supported by the carrier 34. And a gear 22. The carrier 34 is rotatably supported coaxially with the rotation shaft 37 of the sun gear 33, and the output gear 22 is rotatably supported by the carrier 34, and meshes with the sun gear 33 and rotates around the sun gear 33. Revolve. The rotating shaft 37 of the sun gear 33 is fixed to the frame 24 by caulking.
The driving force from the motor M is transmitted to the sun gear 33 via a motor gear 30 fixed to the output shaft of the motor M, a reduction gear 31 for adjusting the rotational speed of the motor M, and an idler gear 32.
The carrier 34 is provided with a rubbing portion 34 c and a leaf spring 36 as friction members that apply a friction load to the sun gear 33. The carrier 34 is rotated according to the forward / reverse rotation direction of the sun gear 33 by the frictional force between the sun gear 33 and the rubbing portion 34c, and the output gear 22 is separated from the roller drive gear 23 that is the driven gear. It has become.
The leaf spring 36 generates a biasing force on the sun gear 33 from the back surface of the rubbing portion 34c, and the leaf spring 36 is positioned and fixed by positioning portions 34d and 34e of the rubbing portion 34c. That is, the plate spring 36 is provided with engagement holes 36b and 36c that engage the positioning portions 34d and 34e, and a pressing piece 36a that is pressed against the rubbing portion 34c.

In the present invention, a counter spring 35 is provided as a biasing member that generates a counter moment M3 that acts in a direction opposite to the self-weight moment M1 of the carrier 34, the output gear 22, the rubbing portion 34c, and the leaf spring 36. The counter spring 35 corresponds to the counter moment member of the present invention.
The self-weight moment M1 is a moment about the rotation shaft 37 generated by the self-weight of the carrier 34, the output gear 22, the rubbing portion 34c, and the leaf spring 36, and is determined by the horizontal distance between the center of gravity position and the center of the rotation shaft 37. . In this example, the gravity center position is located on the roller drive gear 23 side with respect to the vertical line passing through the center of the rotation shaft 37, and the self-weight moment M1 acts in the counterclockwise rotation direction in the figure.
In this example, the friction member 34c and the leaf spring 36, which are friction members, are provided. However, even if there is no friction member, the output gear 22 revolves according to the rotation of the sun gear 33, and the output gear 34 is replaced with the roller drive gear 23. Can be separated. In that case, the self-weight moment is a moment including the carrier 34 and the output gear 22. The self-weight moment is a moment due to the self-weight including the carrier 34 and a heavy object held by the carrier 34.
The counter spring 35 is a tension spring, and is attached in a tensioned state between the spring hook 24a of the frame 24 and the spring hook 34f formed on the carrier 34. Due to its elastic restoring force, the counter moment M3 in the direction opposite to its own weight moment M1 is applied. generate. That is, the spring hook 34f of the carrier 34 serving as a load application point of the counter spring 35 is located on the opposite side of the roller drive gear 23 in the drawing with respect to a vertical line (not shown) passing through the center of the rotation shaft 37. The spring load is applied downward. Due to the spring load of the counter spring 35, the counter moment M3 is applied to cancel the self-weight moment M1 in the opposite direction to the self-weight moment M1, in the clockwise direction CW in the figure.
In addition to canceling the self-weight moment M1, the counter spring 35 generates a moment (hereinafter referred to as a relief moment M4) that causes the output gear 22 to rotate by a gear reaction force state received from the roller drive gear 23 during deceleration. On the other hand, a rotational moment sufficient to maintain the meshing is generated. The degree of the escape moment M4 depends on the deceleration rate and the rotational load of the transport roller 12.
In the present invention, the static friction moment M2 generated by the rubbing portion 34c and the leaf spring 36 is set to be larger than the combined moment of the self-weight moment M1 and the counter moment M3.
The static friction moment M <b> 2 is a moment generated by a static friction force generated at the sliding portion 34 c and is in the opposite direction depending on the rotation direction of the sun gear 33. Assuming that the clockwise direction (CW) is the forward direction and the counterclockwise direction (CCW), the static friction moment M2 is clockwise when rotating in the forward direction and counterclockwise when rotating in the reverse direction. Turning direction (CCW)
Act on.
In the figure, if the clockwise (CW) direction is +, the self-weight moment M1, the static friction moment M2, the counter moment M3, and the relief moment M4 of the carrier 34 during deceleration must satisfy the following relationship. Become.
・ M1 + M2> M3 (Carrier operating condition)
・ M1 + M3 + M4> 0 (Gear tooth skipping condition)
The carrier operating condition is a condition for the output gear 22 to be separated from the roller driving gear 23 during reverse rotation.

Next, with reference to FIGS. 5A and 5B, the operation when the carrier 34 is connected to drive and when the drive is disconnected will be described.
In FIG. 5, a vertical line G and a horizontal line H passing through the rotation center O of the sun gear 33 are drawn in order to explain the operation position. The pendulum gear 22 and the roller drive gear 23 are arranged in a region below the horizontal line on the paper discharge side (left side in the figure) with respect to the vertical line G. The roller drive gear 23 is located at a position slightly lower than the horizontal line H, and the pendulum gear 22 swings between a connection position P1 that contacts and meshes with the roller drive gear 23 and a cutting position P2 that is separated from the roller drive gear 23. Further movement of the cutting position P2 is restricted by the stopper 24b with which the carrier 34 abuts.
The rubbing portion 35c and the leaf spring 36 are located on the opposite side (the right side in the figure) to the paper carry-out side with respect to the vertical line G, but most of the roller drive gear 23 and the carrier 34 are on the left side with respect to the vertical line G. The center of gravity (not shown) is located in a state of being lifted to the left of the vertical line G, and the self-weight moment M1 acts in the direction toward the vertical line G, that is, the counterclockwise direction CCW in the figure.
Further, the counter spring 35 is located on the opposite side (right side in the figure) to the pendulum gear 22 with respect to the vertical line G, and acts on the carrier 34 with a counter moment M3 in the clockwise direction CW in the figure.
FIG. 5A is a diagram at the time of drive connection, and the motor shaft 30 rotates in the counterclockwise direction (CCW) in the drawing. Since the sun gear 33 rotates in the clockwise direction (CW), the carrier 34 is given a static friction moment M2 in the direction E in the drawing by the friction force received from the sliding portion 34c, and the output gear 22 is driven by a roller. Engage with the gear 23. In this state, the tooth surface of the output gear 22 receives the meshing forces F1 and F2 in the pressure angle direction at the contact points with the teeth of the roller drive gear 23. The pressure angle direction is the direction of the action line at the contact point of the tooth surface. This is a force that rotates the carrier 34 in the clockwise direction (CW), and is a force that is generated during acceleration and steady speed.
At the time of deceleration, the rotation direction is the same, but the drive input and output are apparently reversed, and escaping forces F3 and F4 in the direction of mirror movement of F1 and F2 are generated in the output gear 34. These escape forces F3 and F4 also act as a force for rotating the carrier 34 in the counterclockwise direction (CCW). It is necessary for the counter spring 35 to generate a moment to resist this escape force.

Next, with reference to FIG. 5 (B), the operation | movement at the time of cut | disconnecting drive transmission is demonstrated.
The drive transmission is cut off by rotating the motor shaft 30 in the clockwise direction (CW) opposite to that at the time of driving connection. Similar to the drive connection, the carrier 34 generates a static friction moment M2 in the F direction in the figure by the frictional force received from the rubbing portion 34c. In addition, the gear meshing forces F5 and F6 also act in the counterclockwise direction (CCW), so that the separation operation can be performed smoothly. Then, it is fixed at a predetermined position by a stopper 24 b formed on the frame 24.
At this time, when a stepping motor is used as the motor M, hold control after stopping the stepping motor is not performed in the stop control of the stepping motor. This is because the holding operation causes the rubbing portion 34c and the sun gear 33 to vibrate slightly, the frictional force apparently decreases, and a state that does not satisfy M1 + M2> M3 (carrier operating condition) may occur. is there.
Similarly, it is desirable not to perform sudden braking with a reverse voltage even when a DC motor is used.

As described above, according to the first embodiment, it is possible to reduce the operating force during the jam processing by separating the output gear 22 and canceling the inertia of the motor M.
Further, the self-weight moment M1 of the carrier 34 to which the output gear 22, the rubbing portion 34c and the leaf spring 36 are attached can be canceled by the counter moment M3 of the counter spring 35. Therefore, the operation responsiveness at the time of connection and separation can be increased, and the noise at the time of separation can be reduced by shortening the operation time.
Further, since the arrangement of the output gear 22 is not controlled in the direction of gravity due to the addition of the counter spring 35, the degree of freedom of the gear meshing position is improved. Further, the reliability of the operation is improved by matching the direction of the meshing force and the escaping force with the direction of separation of the output gear 22.
In the first embodiment, a tension spring is used as the counter spring 35 as the biasing member. However, a compression spring or a torsion spring may be used, and various biasing forces can be applied to the carrier 34 in the rotational direction. The spring structure can be applied.

[Embodiment 2]
Next, Embodiment 2 of the present invention will be described.
FIG. 6 is a perspective view of a drive unit to which the embodiment of the present invention is applied. In the following description, only the difference in configuration from the first embodiment will be mainly described, and the same components will be denoted by the same reference numerals and description thereof will be omitted.
The carrier 34 has a weight holding portion 34g, and a counterweight 40 is held by the weight holding portion 34g. This counterweight 40 corresponds to the counter moment member of the present invention.
When the moment when the weight of the counterweight 40 is generated is M5,
A weight satisfying M1 + M2> M5 (carrier operating condition) and M1 + M4 + M5> 0 (gear tooth skipping condition) is required for the counterweight 40.
Further, in order to reduce the fluctuation of the moment generated by the counterweight 40, the center of gravity of the counterweight 40 is substantially horizontal with respect to the rotating shaft 37 when the carrier 34 is disposed at an intermediate position between the connection position and the separation position of the carrier 34. It is desirable to hold the counterweight 40 so as to take a position.
The counterweight 40 can be selected from various materials such as a resin and a metal plate, and may be fixed using any one of press-fitting, insert molding, and adhesion methods. Needless to say, the counterweight 40 itself may be integrally formed as a part of the shape of the carrier 34.

In each of the above embodiments, the friction load is applied to the sun gear 33 by the rubbing portion 34c as a friction member and the leaf spring 36, but the friction load is applied to the output gear meshed with the sun gear 33. However, a static friction moment in the direction of rotating the carrier 34 can be applied.
In the above embodiments, the drive transmission mechanism of the present invention is applied to the drive roller pair 12 in the drive transmission unit. However, the other transfer roller pair 14, the upper discharge roller pair 15, the lower discharge The present invention can also be applied to the drive transmission unit of the roller pair 17.
In the above-described embodiment, the configuration in which the drive transmission mechanism of the present invention is applied to the sheet post-processing device 19 has been described. However, the configuration can also be applied to drive transmission units of various conveyance rollers of the image forming apparatus 1. Further, although the sheet post-processing device 19 is configured independently of the image forming apparatus 1, the sheet post-processing device 19 may be integrated as a part of the image forming apparatus 1.
In the above embodiment, the drive transmission unit of the conveyance roller that conveys the paper P of the image forming apparatus has been described as an example. However, the drive transmission unit of the document conveyance roller of the image reading apparatus that reads an image of a sheet-like document. It is also applicable to.
Furthermore, the present invention can be applied not only to a sheet conveying roller but also to a drive transmission unit such as a developing roller, a fixing roller, and a cleaning roller of a developing device.

1 Image forming apparatus 19 Paper post-processing apparatus (sheet processing apparatus)
12 Conveying roller pair, 22 Output gear (Pendulum gear)
23 Roller drive gear (driven gear)
30 Motor shaft 33 Sun gear 34 Carrier 35 Counter spring (counter moment member)
34c Rub (friction member)
36 Leaf spring (friction member)
40 Counterweight (counter moment member)
M1 dead weight moment, M2 static friction moment,
M3 counter moment

Claims (12)

A sun gear to which the driving force from the driving source is transmitted;
A gear holder rotatably supported coaxially with the rotating shaft of the sun gear;
A pendulum gear that is rotatably supported by the gear holder and revolves while rotating in mesh with the sun gear,
In the drive transmission mechanism configured such that the pendulum gear is separated from the driven gear according to the rotation direction of the sun gear,
When the moment about the rotation axis of the sun gear generated by its own weight including the gear holder and the pendulum gear is defined as the self-weight moment, the direction opposite to the self-weight moment with respect to the rotation axis of the sun gear with respect to the gear holder. A drive transmission mechanism comprising a counter moment member that generates a counter moment acting on the motor. A friction member provided on the gear holder and imparting a friction load to the sun gear or the pendulum gear, the self-weight moment is a moment generated by the self-weight including the friction member,
The static friction moment generated around the rotation axis of the sun gear generated by the friction member is larger than the sum of the self-weight moment including the friction member and the counter moment on the gear holder and the pendulum gear. The drive transmission mechanism according to claim 1, which is set.   The drive transmission mechanism according to claim 1, wherein the counter moment member is configured by a biasing member that biases the gear holder.   The drive transmission mechanism according to claim 1 or 2, wherein the counter moment member is constituted by a counterweight provided in the gear holder.   The driven gear from which the pendulum gear is separated is a driving gear fixed to a driving side roller of a pair of conveying rollers for conveying paper, and a driven side roller is pressed against the driving side roller. 5. The drive transmission mechanism according to any one of items 4.   The drive transmission mechanism according to any one of claims 1 to 5, wherein the drive source is a stepping motor, and hold control after the stepping motor is stopped is not performed in the stop control of the stepping motor.   The drive transmission mechanism according to claim 1, wherein the drive transmission mechanism is used for driving transmission to a sheet conveying roller of a sheet processing apparatus connected to the image forming apparatus.   The drive transmission mechanism according to any one of claims 1 to 6, wherein the drive transmission mechanism is used for driving transmission to a sheet conveying roller of the image forming apparatus.   7. The drive transmission mechanism according to claim 1, wherein the drive transmission mechanism is used for driving transmission to a document conveying roller of the image reading apparatus.   A sheet processing apparatus comprising the drive transmission mechanism according to claim 1.   An image forming apparatus to which the sheet processing apparatus according to claim 10 is connected.   An image forming apparatus comprising the drive transmission mechanism according to claim 1.

Images