JP5494149B2 - Transport device - Google Patents

Description

  The present invention is provided between the driving side gear and the driven side gear, and transmits a driving force from the driving source to the feeding roller, and a non-transmitting state in which the driving force is not transmitted from the driving source to the feeding roller. The present invention relates to a transport device provided with a clutch for switching between.

  Generally, a printer device includes a transport device for transporting paper. In addition, the transport device that transports the cut paper employs a structure that allows the recording paper to be inserted and removed as necessary. Here, the driving force of the driving source is transmitted to the feeding roller via the driving side gear and the driven side gear engaged with each other. Therefore, when the user pulls out the paper supplied to the supply port, if the feed roller rotates in the reverse direction, this rotation is transmitted to the drive source via the driven gear and the drive gear.

  Japanese Patent Application Laid-Open No. 2004-228561 proposes a transport apparatus that addresses the above problem using a substantially D-shaped feeding roller in side view. In this transport device, the feeding roller for supplying paper has a shape having a notch portion in which a part of a cylindrical roller is cut out by a plane parallel to the axial direction, that is, a substantially D-shape in side view. doing. Therefore, when it is not necessary to feed the paper, the notch portion of the feeding roller faces the paper, and a gap can be generated between the notch portion and the paper. In this state, even if the paper is pulled out, the feeding roller does not rotate reversely by the paper.

JP 2004-99317 A

  However, when the feeding roller is substantially D-shaped when viewed from the side, the effective circumferential length that can be actually used for feeding paper out of the entire circumference of the feeding roller is a portion excluding the notch. On the other hand, if it is a cylindrical feed roller, the entire circumference can be made the effective circumference. In other words, when a cylindrical feed roller is used, the same effective circumference can be ensured even if the feed roller diameter is reduced, compared to the case of using a substantially D-shaped side view. The size of the apparatus can be reduced.

  However, when a cylindrical feed roller is used, the feed roller contacts the paper even when it is not necessary to feed the paper.Therefore, when the paper is pulled out, the feed roller is reversed due to friction with the paper. Rotated. As described above, if this rotation is transmitted to the driving source via the driven gear and the driving gear, a load may be applied to the driving gear and the driving source via the driven gear.

  By the way, since the conveyance apparatus of patent document 1 is provided with the clutch apparatus which switches ON / OFF of power transmission, if this clutch apparatus is OFF, even if it is a case where a feeding roller is reversely rotated, it will rotate. Is a structure that is not transmitted to the drive side gear and the drive source. However, the rotation due to the reverse rotation of the feeding roller is transmitted to the driven gear and the clutch device. Therefore, there is a possibility that the clutch device and the drive side gear engage with each other as the clutch device rotates.

  SUMMARY OF THE INVENTION An object of the present invention is to provide a transport device that can more reliably suppress the rotation of a feed roller when a sheet is pulled out from a transport device, being transmitted to a drive gear via a driven gear. There is to do.

  The conveying device according to the present invention includes a feeding roller for feeding paper, a driving source for generating a driving force for driving the feeding roller, and between the driving source and the feeding roller. A drive-side gear and a driven-side gear that transmit the driving force to the feed roller; and provided between the drive-side gear and the driven-side gear, from the drive source to the feed roller. A clutch that switches between a transmission state in which the driving force is transmitted and a non-transmission state in which the driving force is not transmitted from the driving source to the feeding roller, and the clutch engages with the driving side gear. Including a clutch main body as a single member formed with both a mating claw and a driven side engaging claw that engages with the driven gear, and when the clutch main body is in a non-engagement position, Driving side engaging claw and front Is engagement release between the driving gear and the engagement of the driven side engaging claw and the driven side gear by being released, the clutch is maintained the on non-transmission state.

  According to the above invention, when the clutch body is in the non-engagement position, the clutch is disengaged from both the drive side gear and the driven side gear. The rotation of the roller is not transmitted to the clutch. For this reason, it is possible to more reliably suppress the rotation of the feeding roller when the paper is pulled out from the conveying device, being transmitted to the driving side gear via the driven side gear.

  In the conveying apparatus according to the present invention, the clutch includes a main body support member having a rotation shaft that rotatably supports the clutch main body, in addition to the clutch main body. The clutch is switched between the transmission state and the non-transmission state by rotating around an axis.

  According to the above invention, since the clutch body is rotated around the rotation shaft to switch the transmission state and non-transmission state of the clutch, the space for arranging the clutch in the axial direction of the rotation shaft is reduced. be able to.

  In the transport device according to the present invention, when the clutch body is in the non-engagement position, the distance between the tooth tip of the driving side gear and the tip of the driving side engaging claw is the same as the tooth tip of the driven gear. It is shorter than the distance from the tip of the driven side engaging claw.

  When the clutch is switched from the non-transmission state to the transmission state, even if the clutch body is rotated, the drive side gear and the drive side engagement pawl may not be engaged and may simply be in contact with each other. When the driven side gear and the driven side engaging claw come into contact with each other before the driving side gear and the driving side engaging claw come into contact with each other, the rotation of the clutch body is prevented by this contact, and each gear engages with each gear. There is a possibility that the nail is not engaged. On the other hand, when the drive side gear and the drive side engagement claw come into contact with each other before the driven side gear and the driven side engagement claw contact, the drive side gear is rotated by the drive source. As the side gear rotates, the gear and the driving side engaging claw engage with each other. The driven side gear and the driven side engaging claw are engaged with each other as the driving side gear and the driving side engaging claw are engaged.

  In the above invention, the distance between the tooth tip of the driving gear and the tip of the driving engagement pawl is shorter than the distance between the tooth tip of the driven gear and the tip of the driven engagement pawl. When the clutch body is rotated for switching to the drive side, the drive side gear and the drive side engagement claw come into contact with each other before the driven side gear and the driven side engagement claw come into contact with each other. Therefore, it is possible to suppress the switching of the clutch from the non-transmission state to the transmission state due to the contact between the driven gear and the driven side engaging claw.

In the conveying device according to the present invention, the number of teeth of the driven side gear is larger than the number of teeth of the driving side gear.
According to the above invention, since the number of teeth of the driven side gear is larger than the number of teeth of the driving side gear, the backlash when the driven side gear and the driven side engaging claw are engaged can be reduced. Further, since the number of teeth of the driving side gear is smaller than the number of teeth of the driven side gear, the strength of the teeth of the driving side gear can be made larger than that of the driven side gear.

The principal part enlarged front view of the printer which concerns on one Embodiment which actualized the conveying apparatus of this invention. FIG. 2 is an AA cross-sectional view of the printer according to the embodiment in FIG. 1. FIG. 3 is an exploded perspective view of a transport device in the printer according to the embodiment. FIG. 2 is an enlarged cross-sectional view of a main part illustrating a transmission state of a conveyance device in the printer according to the embodiment, where (a) is a cross-sectional view taken along line BB in FIG. 1 and (b) is a cross-sectional view taken along line CC in FIG. FIG. 2 is an enlarged cross-sectional view of a main part illustrating a non-transmission state of a conveyance device in the printer according to the embodiment, where (a) is a cross-sectional view taken along line BB in FIG. 1 and (b) is a cross-sectional view taken along line CC in FIG. The principal part enlarged view of FIG. 2 in the state which removed the drive side gear of the printer which concerns on the same embodiment. FIG. 4 is an enlarged view of a main part in a standby state of the printer according to the embodiment, and is a cross-sectional view taken along line BB in FIG. 1. FIG. 2 is an enlarged cross-sectional view of a main part of the printer according to the embodiment when the printer is shifted from a non-transmission state to a transmission state, where (a) is a cross-sectional view taken along line BB in FIG. 1 and (b) is CC in FIG. Sectional drawing. The principal part expanded sectional view of the printer which concerns on the same embodiment just after transfer from a non-transmission state to a transmission state, (a) is BB sectional drawing in FIG. 1, (b) is CC in FIG. Sectional drawing. FIG. 5 is an enlarged cross-sectional view of a main part during a paper feeding operation of the printer according to the embodiment, taken along the line BB of FIG. 1. FIG. 2 is an enlarged cross-sectional view of a main part at the time of transition from a transmission state to a non-transmission state of the printer according to the embodiment, and is a BB cross-sectional view in FIG. FIG. 2 is an enlarged cross-sectional view of a main part immediately after the transition to the non-transmission state of the printer according to the embodiment, and is a BB cross-sectional view in FIG. 1.

  Hereinafter, an embodiment in which the conveyance device of the present invention is mounted on an ink jet printer and embodied will be described with reference to FIGS. In the following description, directions and directions indicated by arrow symbols in the figure are used unless otherwise specified.

  FIG. 1 is an enlarged front view of a main part of a transport device mounted on a printer as viewed from the front of the printer. For convenience of explanation, printer housings and the like that are not directly related to the transport apparatus are omitted. FIG. 2 is a cross-sectional view taken along the line AA in FIG. The positional relationship seen from the side of the member which comprises a conveying apparatus is specified. In addition, in the exploded perspective view shown in FIG. 3, the shape of each component member is clearly shown.

  As shown in FIGS. 1 to 3, the main part of the transport device is rotatably supported by a holder 2 fixed to the printer body. A driving force generated by a motor (not shown) as a driving source is first transmitted to the gear 10. The gear 10 is a composite gear in which a large-diameter gear 11 and a small-diameter gear 12 are formed coaxially and integrally. The driving force transmitted to the gear 10 is transmitted to the driving side gear 40 that meshes with the small diameter gear 12. The driving gear 40 is also a composite gear in which a large-diameter gear 41 and a small-diameter gear 42 are formed coaxially and integrally. The large diameter gear 41 meshes with the small diameter gear 12 of the gear 10. Furthermore, the small-diameter gear 42 of the drive side gear 40 has a structure that can be engaged with and released from the clutch 50. On the other hand, the driven gear 70 is also a composite gear in which a large-diameter gear 71 and a small-diameter gear 72 are formed coaxially and integrally. The small-diameter gear 72 of the driven gear 70 can also be engaged with and released from the clutch 50. The large-diameter gear 71 of the driven gear 70 meshes with the gear 5. Here, the state in which the driving side gear 40 and the clutch 50 are engaged and the driven side gear 70 and the clutch 50 are engaged is the transmission state. In the transmission state, the driving force transmitted to the driving side gear 40 is transmitted to the driven side gear 70 via the clutch 50.

The driving force transmitted to the driven gear 70 is transmitted to the roller drive shaft 80 via the gear 5 meshing with the large diameter gear 71 and the gear 6 meshing with the gear 5.
The roller drive shaft 80 meshes with the gear 7 in the vicinity of the left end portion, a shaft main body 82 that is a rotating shaft extending in the width direction, a right end gear 81 that meshes with the gear 6 disposed at the right end portion. A left end gear 83. A driving force is transmitted to the feeding roller 90 through the gear 7 meshing with the left end gear 83 and the gear 8 meshing with the gear 7.

  The feed roller 90 is a gear 91 that meshes with the gear 8, a roller body 92 that is formed integrally with the gear 91, and rotates coaxially with the gear 91, and a substantially cylindrical friction member that is fitted into the outer peripheral surface of the roller body 92. 93. When the driving force is transmitted to the feeding roller 90, the feeding roller 90 rotates and the paper P that contacts the friction member 93 that rotates integrally is fed. The fed paper is transported by a transport roller R to a lower portion of an unillustrated ejection head, printed, and discharged.

  Next, the clutch 50 will be described in detail with reference to FIGS. 3 and 4. Here, FIG. 4A is a drawing for explaining the state of the driving side gear 40 and the driving side clutch provided in the clutch 50 in the transmission state, and is a cross-sectional view taken along line BB in FIG. FIG. 4B is a drawing for explaining the state of the driven side clutch 70 included in the driven side gear 70 and the clutch 50 in the transmission state, and is a cross-sectional view taken along the line CC in FIG.

  The clutch 50 includes a short cylindrical clutch main body 51 and a main body support member 61 that rotatably supports the clutch main body 51. Specifically, a drive side engagement claw 52 is provided on the right side of the inner peripheral surface of the clutch body 51. The small-diameter gear 42 is inserted from the right side of the clutch body 51 so as to be engageable with the driving-side engaging claw 52. On the other hand, a driven side engaging claw 53 is provided on the left side of the inner peripheral surface of the clutch body 51. The small-diameter gear 72 is disposed so as to be able to engage with the driven-side engagement claw 53 by being inserted from the left side of the clutch main body 51 with the main body support member 61 interposed therebetween. From the outer peripheral surface of the clutch body 51, a bearing portion 56 having a through-hole to be supported by the body support member 61, a body-side spring fixing protrusion 54 to which one end of the spring 69 is fixed, and a transmission state and a non-transmission state A switching projection 55 for switching between the two protrudes radially outward.

  On the other hand, the main body support member 61 is a substantially annular member having a through hole 62 at the center. The small-diameter gear 72 described above is inserted into the through hole 62 from the left, and further inserted into the clutch body 51. A substantially cylindrical rotation shaft 63 projects from the right side surface. The clutch body 51 is rotatably supported by inserting the rotating shaft 63 into the through hole of the bearing portion 56 described above. Further, a support member side spring fixing projection 64 further protrudes from the right side surface, and the other end of the spring 69 is fixed.

  As shown in FIGS. 4A and 4B, the spring 69 is fixed at one end to the main body side spring fixing protrusion 54 provided at the clutch main body 51 and provided at the other end at the main body support member 61. The support member side spring fixing protrusion 64 is fixed. Therefore, as indicated by the black arrows in the drawing, the spring 69 biases the clutch main body 51 in the direction in which the driving side engaging pawl 52 is engaged with the small diameter gear 42 via the main body side spring fixing projection 54. . As a result, if no external force is applied to the clutch body 51, the drive side engagement pawl 52 engages with the small diameter gear 42. Further, as shown in FIG. 4B, the driven side engaging claw 53 is engaged with the small diameter gear 72 by the urging force of the spring 69. The position of the clutch main body 51 at this time is the engagement position, and the clutch 50 is in the transmission state described above when the clutch main body 51 is in the engagement position. When the drive side gear 40 rotates in the transmission state, the clutch main body 51 and the main body support member 61 rotate integrally to transmit the driving force to the driven gear 70.

  On the other hand, as shown in FIG. 5A, when a force opposite to the urging force of the spring 69 is applied to the clutch body 51, the drive side engaging claw 52 is separated from the small diameter gear 42 and the engagement is released. . Further, as shown in FIG. 5B, the driven side engaging claw 53 is also separated from the small diameter gear 72 and the engagement is released. The position of the clutch main body 51 at this time is the non-engagement position, and the clutch 50 is in a non-transmission state when the clutch main body 51 is in the non-engagement position. Thus, in the non-transmission state, not only the drive side gear 40 and the clutch 50 are disengaged but also the driven side gear 70 and the clutch 50 are disengaged. Therefore, even if the drive side gear 40 rotates in the non-transmission state, the clutch body 51 and the body support member 61 do not rotate. Conversely, even if the driven gear 70 rotates, the clutch body 51 and the body support member 61 do not rotate.

Subsequently, a switching lever for switching between the transmission state and the non-transmission state will be described with reference to FIGS. 3 and 6.
The switching lever 30 is a substantially rod-shaped member having a through hole 31 in the center. A switching claw 33 that engages with the switching protrusion 55 of the clutch body is provided in front of the through hole 31. An abutting portion 32 that abuts on the carriage 1 is formed at the tip of the switching lever 30 in front of the switching claw 33. The switching lever 30 is connected to the printer body via the lever driving gear 20.

  Here, as shown in FIG. 3, the lever driving gear 20 includes a gear main body 21 and a cylindrical portion 22 extending leftward from the gear main body 21. The cylindrical portion 22 is inserted into the through hole 31 such that the outer peripheral surface of the cylindrical portion 22 is in sliding contact with the inner peripheral surface of the through hole 31 of the switching lever 30, and a further tip of the cylindrical portion 22 is provided in the printer main body (not shown). It is inserted in the concave part. Accordingly, the switching lever 30 is supported so as to be rotatable about the lever driving gear 20 as a rotation center.

  Furthermore, since the gear main body 21 of the lever drive gear 20 meshes with the large-diameter gear 11 of the gear 10, it rotates in conjunction with the gear 10. Further, since the through hole 31 is in sliding contact with the outer peripheral surface of the cylindrical portion 22, the switching lever 30 receives a force and rotates when the lever driving gear 20 rotates.

  Specifically, as indicated by the black arrow in FIG. 6, when the gear 10 rotates forward, the lever driving gear 20 also rotates forward, so that the switching lever 30 moves the switching claw 33 closer to the clutch body 51. Rotate. When the clutch 50 rotates in this state, the switching claw 33 engages with the switching protrusion 55, so that a force is applied to the clutch body 51, and the clutch 50 is switched to the non-transmission state.

  As indicated by the white arrow in FIG. 6, when the gear 10 rotates in the reverse direction, the lever drive gear 20 also rotates in the reverse direction. Then, since the engagement between the switching claw 33 and the switching protrusion 55 is released, the force applied to the clutch body 51 disappears. As a result, the clutch 50 is switched to the transmission state by the urging force of the spring 69.

  Further, when the carriage 1 is positioned rightward in the width direction, the contact portion 32 contacts the rear portion of the carriage 1 as shown in FIG. The rotation of the switching lever 30 in the direction to be locked is locked. In this case, even if the gear 10 rotates in the reverse direction, the non-transmission state is not switched to the transmission state.

  The sheet feeding operation by the transport device will be described with reference to FIGS. 5 and 7 to 12. More specifically, the driving side gear 40 (more specifically, the small diameter gear 42) and the driving side engagement are shown in FIGS. The relationship with the claw 52 will be mainly described. 5 (b), FIG. 8 (b), and FIG. 9 (b), the relationship between the driven side gear 70 (more specifically, the small diameter gear 72) and the driven side engaging claw 53 will be mainly described.

  As shown in FIG. 5, the clutch 50 is in a non-transmission state in a standby state before starting feeding. As already described, when the switching claw 33 of the switching lever 30 is engaged with the switching projection 55, the driving side engaging claw 52 is separated from the small diameter gear 42 and the driven side engaging claw 53 is separated from the small diameter gear 72. And are separated. Further, since the carriage 1 is located on the right side, the switching lever 30 is locked. Therefore, in this state, the clutch 50 does not switch to the transmission state.

  As shown in FIG. 7, when the carriage 1 moves to the left, the lock of the switching lever 30 is released. When the gear 10 is rotated in reverse in this state, the engagement between the switching claw 33 and the switching protrusion 55 is released as described above.

  As shown in FIG. 8A, the clutch main body 51 is rotated by the biasing force of the spring 69 by the switching lever 30, so that the small-diameter gear 42 of the driving side gear 40 and the driving side engaging claw 52 are engaged. . Here, the distance between the tip of the driving side engaging claw 52 and the tip of the gear tooth of the small diameter gear 42 of the driving side gear 40 is the gear tooth of the small diameter gear 72 of the driven side engaging claw 53 and the driven side gear 70. Therefore, the small-diameter gear 42 of the driving side gear 40 and the driving side engaging claw 52 are engaged first. Therefore, as shown in FIG. 8B, the small diameter gear 72 of the driven side gear 70 and the driven side engaging claw 53 are close to each other but not yet engaged.

  By adopting such a configuration, even if the engagement is hindered by the contact between the tip of the drive-side engagement claw 52 and the tip of the gear tooth of the small-diameter gear 42, the small-diameter gear 42 rotates. Therefore, the contact between the tips of the teeth is released and the state can be shifted to the engaged state. After that, even when the engagement is hindered by the contact between the tip of the driven side engaging claw 53 and the tip of the gear tooth of the small diameter gear 72, the clutch 50 has already been rotated. The contact is released and the state can be shifted to the engaged state.

  As shown in FIGS. 9A and 9B, following the engagement of the small diameter gear 42 of the drive side gear 40 and the drive side engagement claw 52, the small diameter gear 72 of the driven side gear 70 and the driven side engagement are engaged. When the claw 53 is engaged, the transmission state is entered.

  Since the number of teeth of the small diameter gear 72 of the driven side gear 70 is larger than the number of teeth of the small diameter gear 42 of the driving side gear 40, the backlash of the driven side gear 70 is larger than that of the driving side gear 40. It is getting smaller.

  In the transmission state, the driving force of the driving side gear 40 is transmitted to the driven side via the clutch 50, so that as shown in FIG. 10, all of the driving side gear 40, the clutch 50, and the driven side gear 70 are Rotate. As a result, the feeding roller 90 rotates via the gears 5 and 6, the roller drive shaft 80, and the gears 7 and 8, thereby feeding the paper.

  By the way, since the gear 10 is rotating forward when the paper is being fed, the switching lever 30 is rotated via the meshing lever driving gear 20, and the switching claw 33 comes close to the clutch body 51. . When the clutch 50 makes one rotation in this state, the switching claw 33 of the switching lever 30 is engaged with the switching protrusion 55 again as shown in FIG.

  When the clutch 50 further rotates, the switching protrusion 55 is pressed against the switching claw 33 as shown in FIG. Therefore, a force opposite to the biasing force of the spring 69 is applied to the clutch body 51, so that the driving side engaging claw 52 is separated from the small diameter gear 42 and the driven side engaging claw 53 is separated from the small diameter gear 72. Is done.

  As a result, the clutch 50 enters a non-transmission state, and the paper feeding is completed. Thereafter, when the carriage 1 moves to the right and the switching lever 30 is locked, the standby state shown in FIG. 5 is restored.

According to the above embodiment, the following effects can be obtained.
(1) In the above embodiment, when the clutch main body 51 is in the non-engagement position, the clutch 50 is disengaged from both the drive side gear 40 and the driven side gear 70, so that the paper is pulled from the transport device. The rotation of the feeding roller 90 when it is pulled out is not transmitted to the clutch 50. For this reason, it is possible to more reliably suppress the rotation of the feeding roller 90 when the sheet is pulled out from the transport device to the driving side gear 40 via the driven side gear 70. Therefore, as a result of the clutch 50 and the drive side gear 40 being unintentionally engaged by the rotation of the clutch 50, it is possible to prevent a load from being applied to the drive side gear 40 and the motor that is the drive source.

  (2) In the above embodiment, since the clutch main body 51 rotates around the rotation shaft 63, the transmission state and non-transmission state of the clutch are switched, so that the clutch is arranged in the axial direction of the rotation shaft 63. Space can be reduced.

  (3) In the above embodiment, the distance between the tooth tip of the small diameter gear 42 of the driving side gear 40 and the tip of the driving side engaging claw 52 is equal to the tooth tip of the small diameter gear 72 of the driven side gear 70 and the driven side engaging claw 53. It is shorter than the distance to the tip. Therefore, when the clutch main body 51 is rotated for switching from the non-transmission state to the transmission state, the driving side gear 40 is moved before the small diameter gear 72 of the driven side gear 70 and the driven side engaging claw 53 come into contact with each other. The small-diameter gear 42 and the driving side engaging claw 52 come into contact with each other. Accordingly, it is possible to suppress the switching of the clutch 50 from the non-transmission state to the transmission state due to the contact between the small diameter gear 72 of the driven side gear 70 and the driven side engaging claw 53.

  (4) In the above embodiment, since the number of teeth of the small diameter gear 72 of the driven side gear 70 is larger than the number of teeth of the small diameter gear 42 of the driving side gear 40, the small diameter gear 72 of the driven side gear 70 and the driven side engaging claws. The backlash when 53 is engaged can be reduced. Further, since the number of teeth of the small diameter gear 42 of the driving side gear 40 is smaller than the number of teeth of the small diameter gear 72 of the driven side gear 70, the strength of the teeth of the small diameter gear 42 of the driving side gear 40 is set to be small. It can be larger than 72.

In addition, you may change the said embodiment as follows.
In the above embodiment, the number of teeth of the small diameter gear 72 of the driven side gear 70 is larger than the number of teeth of the small diameter gear 42 of the driving side gear 40, but if the backlash can be reduced by other methods, The number of teeth of the small diameter gear 72 of the gear 70 and the number of teeth of the small diameter gear 42 of the drive side gear 40 may be the same, or the number of teeth of the small diameter gear 42 of the drive side gear 40 may be increased.

  In the above embodiment, the distance between the tip of the driving side engaging claw 52 and the tip of the gear tooth of the small diameter gear 42 of the driving side gear 40 is the same as the distance between the tip of the driven side engaging claw 53 and the small diameter gear 72 of the driven side gear 70. Although it is configured to be shorter than the distance from the tip of the gear teeth, other configurations may be used. For example, the shape of the tip of the driven side engaging claw 53 and the shape of the tip of the gear tooth of the small-diameter gear 72 are configured by curves, and even if the tip of the gear and the tip of the claw are in contact, the tips slide with each other. Thus, by adopting a configuration in which the contact state can be released, it is possible to avoid a state in which each gear and each engagement claw are not engaged.

  In the above embodiment, the clutch main body 51 has a short cylindrical shape and has the driving side engaging claw 52 and the driven side engaging claw 53 on the inner peripheral surface, but may have other configurations. Any configuration may be used as long as the clutch main body 51 rotates around the rotation shaft 63 so that the transmission state and the non-transmission state can be switched. For example, the driving-side engaging claw and the driven-side engaging claw may be on the outer peripheral surface, and the driving-side gear and the driven-side gear may be internal gears and may surround the clutch body from the outer peripheral direction.

  In the above embodiment, the transport device is embodied as a transport device mounted on an ink jet printer, but may be mounted on other equipment. For example, the printer may be mounted on another type of printer such as a laser printer, or may be mounted on other equipment that transports paper, other than a printer such as a scanner or a fax machine.

  P ... paper, R ... conveying roller, 1 ... carriage, 2 ... holder, 5 ... gear, 6 ... gear, 7 ... gear, 8 ... gear, 10 ... gear, 11 ... large diameter gear, 12 ... small diameter gear, 20 ... Lever drive gear, 21 ... gear body, 22 ... cylindrical part, 30 ... switch lever, 31 ... through hole, 32 ... contact part, 33 ... switching claw, 40 ... drive side gear, 41 ... large diameter gear, 42 ... small diameter Gear: 50 ... Clutch, 51 ... Clutch body, 52 ... Drive side engaging claw, 53 ... Drive side engaging claw, 54 ... Body side spring fixing projection, 55 ... Switching projection, 56 ... Bearing, 61 ... Body support member , 62 ... through-hole, 63 ... rotating shaft, 64 ... support member side spring fixing projection, 69 ... spring, 70 ... driven side gear, 71 ... large diameter gear, 72 ... small diameter gear, 80 ... roller drive shaft, 81 ... Right end gear, 82 ... shaft body, 83 ... left end gear, 90 ... feed roller, 9 ... gear, 92 ... the roller body, 93 ... friction member.

Claims (4)

A feeding roller for feeding paper,
A driving source for generating a driving force for driving the feeding roller;
A driving side gear and a driven side gear, which are provided between the driving source and the feeding roller and transmit the driving force to the feeding roller;
Provided between the driving side gear and the driven side gear to transmit the driving force from the driving source to the feeding roller and not to transmit the driving force from the driving source to the feeding roller A clutch that switches between a non-transmission state and
The clutch includes a clutch body as a single member in which both a driving side engaging claw that engages with the driving side gear and a driven side engaging claw that engages with the driven side gear are formed. Yes,
When the clutch body is in the non-engagement position, the engagement between the drive side engagement claw and the drive side gear is released, and the engagement between the driven side engagement claw and the driven side gear is released. Thus, the conveying device in which the clutch is maintained in the non-transmission state. In the conveyance apparatus of Claim 1,
In addition to the clutch body, the clutch includes a body support member having a rotation shaft that rotatably supports the clutch body.
The conveyor body is configured to switch the transmission state and the non-transmission state of the clutch by rotating around the rotation shaft. In the conveyance apparatus of Claim 2,
When the clutch body is in the non-engagement position, the distance between the tooth tip of the driving gear and the tip of the driving engagement pawl is such that the tooth tip of the driven gear and the tip of the driven engagement pawl are Conveyor shorter than the distance. In the conveyance apparatus as described in any one of Claims 1-3,
A conveying device in which the number of teeth of the driven gear is greater than the number of teeth of the driving gear.

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