JP5136785B2 - GEAR DEVICE AND RECORDING DEVICE HAVING THE SAME - Google Patents

Description

  The present invention relates to a gear device including a transmitted gear to which power is transmitted and a power transmission gear that can be engaged with and released from the transmitted gear by planetary movement around a drive gear. The present invention also relates to a recording apparatus represented by a facsimile, a printer, etc., provided with the gear device.

A power transmission gear (planetary gear) that can mesh and release meshing with the transmitted gear by planetary motion is provided, and power transmission to the transmitted gear is switched on and off via the planetary motion of the power transmission gear. A gear device to be used has been widely used conventionally (see, for example, Patent Document 1).
JP 2008-74582 A

  However, depending on the positional relationship between the power transmission gear and the transmitted gear, the rotation direction of the transmitted gear when the power transmission gear attempts to separate from the transmitted gear may be a direction that inhibits the separation of the power transmission gear. As a result, the teeth of the power transmission gear may be engaged with the teeth of the transmitted gear, and the power transmission gear may not be separated from the transmitted gear. In particular, when the power transmission gear is going to be separated from the transmitted gear, if the transmitted gear is further rotated for a reason other than the rotational action received from the power transmission gear, the power transmission gear is further separated from the transmitted gear. Cannot be separated.

  Therefore, the present invention has been made in view of such a situation, and the purpose of the present invention is that when the power transmission gear is going to be separated from the transmitted gear, the transmitted gear holds the power transmission gear by its rotation. In particular, the power transmission gear is reliably separated from the transmitted gear even when the transmitted gear is rotated in the rotational direction that promotes the retention.

  In order to solve the above-described problem, the gear device according to the first aspect of the present invention is provided so as to mesh with a transmitted gear to which power is transmitted and a drive gear and to be capable of planetary motion around the drive gear, A power transmission gear that meshes with the transmitted gear when the drive gear rotates in the first direction, and that separates from the transmitted gear when the drive gear rotates in the second direction; and that meshes with the transmitted gear and the transmitted gear And the power transmission gear is separated from the power transmission gear when the drive gear rotates in the first direction, and the power transmission gear is separated from the first direction rotation of the drive gear. And an auxiliary gear that meshes with the power transmission gear in accordance with switching to the second direction rotation and applies a force in a direction away from the transmitted gear to the power transmission gear by the rotation. That.

  According to this aspect, when the drive gear is switched from the first direction rotation to the second direction rotation, the drive gear meshes with the power transmission gear (planetary gear) to apply a force in a direction away from the transmitted gear to the power transmission gear. Since the auxiliary transmission gear is provided, when the power transmission gear tries to be separated from the transmitted gear, it is possible to prevent the transmitted gear from holding the power transmission gear due to the rotation thereof. Can be reliably separated from the transmitted gear even when it is rotated in the rotational direction to promote the retention.

The gear device according to a second aspect of the present invention is characterized in that, in the first aspect, the auxiliary gear is provided with means for generating a resistance force in a displacement direction thereof.
According to this aspect, since the gear device according to the second aspect includes the means for generating a resistance force in the displacement direction of the auxiliary gear, the auxiliary gear can be prevented from inadvertently moving. Specifically, for example, the drive gear rotates in the first direction and the auxiliary gear engages with the power transmission gear in a state where the power transmission gear drives the gear to be transmitted. It can prevent that rotation is inhibited.

  The gear device according to a third aspect of the present invention is the gear device according to the second aspect, wherein the means for generating the resistance force is in a direction of a straight line connecting the rotation center of the auxiliary gear and the rotation center of the transmitted gear. The resistance force is applied to the auxiliary gear on the side far from the transmitted gear with respect to the rotation center of the auxiliary gear.

  According to this aspect, the auxiliary gear rotates in an unintended direction, that is, the drive gear rotates in the first direction by the rotational action centered on the position where the resistance force is applied, and the power transmission gear drives the transmitted gear. In this state, it is possible to prevent the auxiliary gear from moving in a direction to engage with the power transmission gear.

  According to a fourth aspect of the present invention, in the first to third aspects, when the transmitted gear receives a rotational torque from the power transmission gear, the gear device receives power from the transmitted gear accordingly. Rotating torque is transmitted to the rotating shaft, and when the transmission of the rotating torque from the power transmission gear is cut off, there is provided locking means for locking the rotating shaft in response thereto.

  According to this aspect, the power transmission gear includes the locking means that locks the rotation shaft that is driven by the transmitted gear in a state where the power transmission gear does not transmit power to the transmitted gear. In a state where no power is transmitted to the gear, it is possible to prevent the transmitted gear from being rotated from a driving target driven by the transmitted gear.

  A gear device according to a fifth aspect of the present invention is the gear device according to the fourth aspect, wherein the locking means rotates integrally with the rotary shaft and is displaceable in the axial direction of the rotary shaft; A lock member provided in a fixed state that engages with the clutch member to restrict rotation of the clutch member, a biasing member that biases the clutch member toward the lock member, and the transmitted gear are integrated. And a boss that is loosely inserted into a cam groove provided on an outer peripheral portion of the clutch member, and a torque transmission member that transmits rotational torque to the clutch member via the boss. The boss is displaced in the cam groove in accordance with the switching of rotation / stop of the torque transmitting member, so that the boss resists the urging force of the urging member and causes the clutch member to move. The lock release state in which the lock member is separated from the lock member and the lock state in which the boss allows the clutch member to displace and the clutch member is engaged with the lock member are switched. And According to this aspect, the structure of the locking means can be simplified and the cost can be reduced.

  A gear device according to a sixth aspect of the present invention is the gear device according to the fifth aspect, wherein the gear device meshes with the drive gear and is provided so as to be capable of planetary movement around the drive gear, and when the drive gear rotates in the second direction, A second power transmission that meshes with the transmitted gear and rotationally drives the transmitted gear in a direction opposite to the rotational driving direction of the power transmitting gear and is separated from the transmitted gear when the driving gear rotates in the first direction. Using a power cutting time that is generated when the rotational direction of the drive gear is switched and the transmitted gear does not mesh with either the power transmission gear or the second power transmission gear. The rotating shaft is locked.

  According to this aspect, the rotation shaft is adjusted by the locking means by using the power cutting time that occurs when the rotation direction of the drive gear is switched and the transmitted gear does not mesh with either the power transmission gear or the second power transmission gear. Since the locking is performed, the rotating shaft can be locked when the rotating direction is switched while enabling both the forward and reverse rotational driving of the rotating shaft.

  According to a seventh aspect of the present invention, there is provided a recording apparatus for recording on a recording medium, and a recording medium provided on the upstream side of the recording means in a conveyance path of the recording medium, and the recording medium is disposed on the recording means side. A first feed roller that transports the recording medium to the upstream side of the first feed roller in the transport path of the recording medium, and a second feed roller that transports the recording medium to the first feeding roller side; The first feeding roller and the second feeding roller are configured to be rotationally driven by a common drive motor, and a rotational torque from the first feeding roller to the second feeding roller. The transmission path is provided with the gear device according to any of the fourth to sixth aspects, and is configured such that the rotation shaft of the second feed roller can be locked by the locking means provided in the gear device. Be

  According to this aspect, the gear device according to any one of the fourth to sixth aspects enables execution of the biting discharge type skew removal using the first feed roller and the second feed roller, and the second Since the rotation shaft of the feed roller is locked by the locking means, the second feed roller is applied to the recording medium when bending a strong recording medium such as thick paper between the first feed roller and the second feed roller. It can prevent being turned easily.

  Hereinafter, embodiments of the present invention will be described with reference to FIGS. 1 to 10. FIG. 1 is a side sectional view showing a sheet conveyance path of an ink jet printer (hereinafter referred to as “printer”) 1 as an embodiment of a recording apparatus, and FIGS. 2 to 4 are views of a gear device 8 according to an embodiment of the present invention. FIG. 5 and FIG. 6 (A) are partially enlarged views around the first planetary gear 95, and FIG. 6 (B) is a view showing a mounting structure of the auxiliary gear 98. FIG. 7 is an exploded perspective view of the locking means 70, and FIG. 8 is an enlarged perspective view (partially sectional view) of main parts of the locking means 70, FIGS. 9A, 9B, 10A, and 10B. ) Is a cross-sectional view of the locking means 70 cut along a plane parallel to the axial direction of the rotary shaft 71a.

<< 1. Configuration of recording device >>
The overall configuration of the printer 1 will be outlined below with reference to FIG. Note that FIG. 1 illustrates the rollers arranged on the paper conveyance path of the printer 1 so that almost all the rollers are drawn on the same surface, but the position in the depth direction (the front and back sides of the paper in FIG. 1). Do not necessarily match (sometimes match).

  The printer 1 includes a feeding device 2 at the bottom of the device, feeds recording paper P as a recording medium one by one from the feeding device 2, performs ink jet recording in the recording means 4, and the front side of the device (see FIG. 1 is provided to discharge toward a paper discharge stacker (not shown) provided on the right side). The printer 1 also has a duplex unit 7 detachably attached to the rear part of the apparatus. The printer 1 is curved and inverted so that the second surface opposite to the first surface of the first recording sheet P faces the recording head 42. As a result, recording can be performed on both sides of the paper P.

  Hereinafter, each component will be further described. The feeding device 2 includes a paper cassette 11, a pickup roller 16, a guide roller 20, and a separating unit 21. A paper cassette 11 capable of storing a plurality of paper sheets P in a stacked state is configured to be attached to and detached from the front side of the apparatus main body of the feeding apparatus 2, and is a pickup that is rotationally driven by a motor (not shown). The roller 16 is provided on a swinging member 17 that swings about a swinging shaft 18, and rotates in contact with the paper stored in the paper cassette 11, thereby sending the uppermost paper P from the paper cassette 11. .

  A separating member 12 is provided at a position facing the leading edge of the paper stored in the paper cassette 11, and the leading edge of the uppermost paper P to be fed advances downstream while sliding on the separating member 12. First-stage separation from the next and subsequent sheets P is performed. A free-rotating guide roller 20 is provided on the downstream side of the separating member 12, and further, on the downstream side thereof, the second stage separation of the paper P, which includes the separation roller 22 and the driving roller 23, is performed. Separation means 21 is provided.

  On the downstream side of the separating unit 21, a driving roller 26 that is rotationally driven by a motor (not shown) and an assist roller 27 that is driven to rotate by nipping the paper P between the driving roller 26 are configured. A first intermediate feeding unit 25 is provided, and the first intermediate feeding unit 25 feeds the paper P further downstream. Reference numeral 29 denotes a driven roller that reduces a paper passing load when the paper P passes through the curved inversion path (particularly when the paper trailing edge passes).

  On the downstream side of the driven roller 29, a driving roller 32 that is rotationally driven by a motor (not shown) and an assist roller 33 that is driven to rotate while the paper P is nipped between the driving roller 32 are configured. A second intermediate feeding unit 31 is provided, and the sheet P is further fed downstream by the second intermediate feeding unit 31.

  The recording unit 4 is disposed on the downstream side of the second intermediate feeding unit 31. The recording unit 4 includes a conveying unit 5, a recording head 42, a paper guide front 39, and a discharging unit 6. The conveyance means 5 includes a conveyance drive roller 35 that is rotationally driven by a motor (not shown), and a conveyance driven roller 36 that is pivotally supported on the paper guide 37 so as to be driven to rotate while being pressed against the conveyance drive roller 35. The paper P is precisely fed toward the position facing the recording head 42 by the transport means 5.

  Note that the skew of the recording sheet P fed from the feeding device 2 is removed by the biting discharge type skew removal control using the first feeding roller and the second feeding roller on the upstream side thereof.

  Specifically, after the leading edge of the recording paper P is bitten between the transport driving roller 35 (first feed roller) and the transport driven roller 36 and sent to the downstream side by a predetermined amount (FIG. 2), the upstream side With the drive roller 32 (second feed roller) stopped, the transport drive roller 35 is reversed (FIG. 2 → FIG. 3), and the leading edge of the sheet is discharged upstream of the transport drive roller 35 (FIG. 3 → FIG. 4). As a result, the sheet P bends between the driving roller 32 and the conveyance driving roller 35, the leading end of the sheet P follows the nip point between the conveyance driving roller 35 and the conveyance driven roller 36, and the skew is corrected (FIG. 4).

  Subsequently, the recording head 42 is provided at the bottom of the carriage 40. The carriage 40 is guided in the main scanning direction by a motor (not shown) while being guided by a carriage guide shaft 41 extending in the main scanning direction (the front and back direction in FIG. 1). Driven to reciprocate. A pre-paper guidance 39 is provided at a position facing the recording head 42, and the distance between the paper P and the recording head 42 is defined by the pre-paper guidance 39.

  The discharge means 6 provided on the downstream side of the paper guide front 39 includes a discharge drive roller 44 that is rotationally driven by a motor (not shown), and a discharge driven roller 45 that is driven to rotate in contact with the discharge drive roller 44. The sheet P that is configured and recorded by the recording unit 4 is discharged by the discharge unit 6 to a stacker (not shown) provided on the front side of the apparatus.

  The duplex unit 7 includes a large-diameter reversing roller 46 and assist rollers 47 and 48 that are driven to rotate while the paper P is nipped between the reversing roller 46. The sheet P that has been fed out from the sheet cassette 11 and recorded on the first surface is recorded on the first surface by the reverse feeding operation of the second intermediate feeding unit 31, the conveying unit 5, and the discharging unit 6. The side that was the trailing edge of the paper at the time becomes the leading edge, and is drawn between the reversing roller 46 and the assist roller 48.

  The reversing roller 46 is rotationally driven in a counterclockwise direction in FIG. 1 by a motor (not shown), and a sheet of paper drawn between the reversing roller 46 and the assist roller 48 includes a reversing roller 46 and an assist roller 47. The second intermediate feeding section 31 is reached again through the interval, and is guided to the recording means 4, and thereafter recording is similarly performed.

  Note that the pickup roller 16, drive rollers 23, 26, and 32, the conveyance drive roller 35, the discharge drive roller 44, and the reverse roller 46 that are provided in the sheet conveyance path described above are all the same in rotation. It is configured to be rotationally driven by a drive motor. Among these, the gear device 8 according to the present invention is provided between the drive roller 32 and the drive motor constituting the second intermediate feed portion 31.

<< 2. Overall configuration of gear device >>
Hereinafter, the gear device 8 according to an embodiment of the present invention will be described with reference to FIGS. 2 to 10. In FIG. 2, reference numeral 61 denotes a side frame (which constitutes a base body of the printer 1) that forms a surface parallel to the paper conveyance direction, and the gear device 8 is provided on the side frame 61. 2 constitutes a gear device 8 according to one embodiment of the present invention.

  In FIG. 2, reference numeral 90 denotes a gear provided at the shaft end of the conveyance driving roller 35, and rotational torque is transmitted from the gear 90 to the driving gear 94, and rotational torque is transmitted from the locking means 70 to the gear 97. Communicated. The gear 97 is attached to the shaft end of the rotary shaft 32a of the drive roller 32 described above, and the lock means 70 constituting the gear device 8 is in an unlocked state that allows the rotation of the rotary shaft 32a and rotates. Switches between the lock states to be restricted.

  Further, a tooth wheel train (not shown) is further provided on the left side of the gear 97 in FIG. 2, and the rotation torque of the transport drive roller 35 (drive motor) is transmitted via the gear 97 to the reversing device 7 (reversing roller). 46).

  Hereinafter, the configuration of the gear device 8 will be further described in detail. As shown in FIGS. 2 to 4, the gear device 8 includes a drive gear 94, a first planetary gear 95 as a “power transmission gear (first power transmission gear)”, a first planetary lever 77, and a “second planetary gear”. A second planetary gear 96 as a “power transmission gear”, a second planetary lever 78, and a lock means 70 are provided. The lock means 70 includes a gear 71, a clutch member 72, a lock member 73, a coil spring 74 as an urging member, and a torque transmission member 75.

  The first planetary gear 95 and the second planetary gear 96 are pivotally supported by a first planetary lever 77 and a second planetary lever 78 that can swing around the rotation center of the drive gear 94, respectively. The drive gear 94 is engaged. The first planetary lever 77 and the second planetary lever 78 perform a swinging motion with the rotation of the drive gear 94 so that the drive gear 94 is moved around in a planetary motion.

  By this planetary motion, it is possible to displace between a meshing position where each meshes with the transmitted gear 75b and a separated position spaced from the transmitted gear 75b. 2 and 3 show a state in which the first planetary gear 95 is in the meshing position and the second planetary gear 96 is in the separated position. FIG. 4 shows that both the first planetary gear 95 and the second planetary gear 96 are in contact with each other. A state of being in the separated position is shown. The state in which the second planetary gear 96 is in the meshing position is not shown.

  In the present embodiment, for the sake of convenience, the conveyance drive roller 35 (gear 90) is normally rotated when it rotates in the clockwise direction of FIG. 2 (when the paper P is conveyed downstream), and the counterclockwise of FIG. When the sheet rotates in the turning direction (when the paper P is conveyed upstream), the reverse rotation is assumed.

  The first planetary gear 95 is displaced to the meshing position as shown in FIG. 2 along with the forward rotation of the transport drive roller 35 (rotation of the drive gear 94 in the first direction), and the transmitted gear 75b is rotated counterclockwise in FIG. Rotate in the direction. Further, as the conveyance drive roller 35 reverses (rotation of the drive gear 94 in the second direction), it is displaced to the separation position as shown in FIG.

  On the contrary, the second planetary gear 96 is displaced to the meshing position with the reverse rotation of the transport drive roller 35 (rotation of the drive gear 94 in the second direction) and rotationally drives the transmitted gear 75b in the clockwise direction of FIG. Not shown). Further, as the conveyance drive roller 35 rotates forward (rotation of the drive gear 94 in the first direction), it is displaced to a separated position as shown in FIG.

  2 to 4, the gear 71 and the transmitted gear 75 b have the same outer diameter and rotate around the same center of rotation, so that they are depicted as overlapping, but actually, as shown in FIG. 7. The gear 71 is located on the front side of FIGS. 2 to 4, and the transmitted gear 75 b is located on the back side of FIGS. 2 to 4. That is, in FIGS. 2 to 4, the gear 71 meshes only with the gear 97, and does not mesh with the first planetary gear 95 and the second planetary gear 96 described later. The transmitted gear 75 b meshes only with the first planetary gear 95 or the second planetary gear 96, and does not mesh with the gear 97.

<< 3. Configuration of locking means >>
Next, the locking unit 70 will be described in detail. The function of the locking means 70 is generally that when the transmitted gear 75b receives a rotational torque from the first planetary gear 95 or the second planetary gear 96, the gear 71 (rotating shaft 71a) is allowed to rotate accordingly. At the same time, when the gear 71 is rotated and the transmission of the rotational torque from the first planetary gear 95 or the second planetary gear 96 is cut off (the transmitted gear 75b is connected to either the first planetary gear 95 or the second planetary gear 96). The gear 71 (the rotating shaft 71a) is locked in response to this.

  As shown in FIG. 7, the clutch member 72 includes a hole 72 e through which a rotary shaft 71 a formed integrally with the gear 71 is inserted. The rotary shaft 71a has a cross-shaped cross-sectional shape, and the hole 72e through which the rotary shaft 71a is inserted is formed to have a cross-shaped shape in the same manner as the rotary shaft 71a along the cross-sectional shape. . Therefore, when the clutch member 72 rotates, the gear 71 receives rotational torque from the clutch member 72 and rotates together with the clutch member 72.

  The rotating shaft 71a and the hole 72e are in an unconstrained relationship in the axial direction of the rotating shaft 71a, that is, the clutch member 72 is provided so as to be slidable in the axial direction of the rotating shaft 71a.

  The clutch member 72 has a cam groove 72b formed on the outer peripheral portion thereof, and a meshing tooth 72a is formed at a position facing the lock member 73 in the assembled state of the gear device 8 (FIGS. 8 to 8). 10).

  The rotary shaft 71a has a cross-shaped cross section until reaching the tip portion, but the tip portion is formed in a columnar shape, and the lock member 73 can freely rotate the tip portion of the rotary shaft 71a. A hole 73b is formed to be received. In the assembled state of the gear device 8, meshing teeth 73 a are formed at positions facing the meshing teeth 72 a formed on the clutch member 72. The lock member 73 is fixed to the side frame 61.

The coil spring 74 is interposed between the gear 71 and the clutch member 72, and biases the clutch member 72 toward the lock member 73.
The torque transmission member 75 has an annular shape that accommodates the clutch member 72 therein in the assembled state of the gear device 8, and is integrally provided with a transmitted gear 75b on the outer periphery thereof. By meshing with the first planetary gear 95 or the second planetary gear 96, the rotational torque from the drive motor is transmitted to rotate.

  As described above, the clutch member 72 is provided so as to rotate integrally with the rotation shaft 71a (gear 71). However, the torque transmission member 75 is relative to the clutch member 72 and the rotation shaft 71a (gear 71). Therefore, it can be rotated by a certain rotation angle (detailed later).

  Two bosses 75a are formed on the inner peripheral surface of the torque transmission member 75 at positions facing each other on the inner periphery so as to form a phase of 180 °, and the boss 75a is assembled in the assembled state of the gear device 8. As shown in phantom lines in FIG. 8, and as shown in FIGS. 9 and 10, the cam grooves 72b formed in the clutch member 72 (two positions are formed similarly to the boss 75a) are loosely inserted. ing.

  The cam groove 72b allows a certain amount of movement (a certain amount of rotation of the torque transmission member 75) in the circumferential direction of the boss 75a in the cam groove, and also the axial direction of the rotation shaft 71a of the boss 75a (upper and lower in FIG. 8). It has a shape that allows movement in the direction). More specifically, it has side walls 72c and 72c that form surfaces substantially perpendicular to the axial direction of the rotation shaft 71a, and slopes 72d and 72d that are inclined with respect to the side walls 72c and 72c.

  The operation of the lock means 70 configured as described above will be described below with reference to FIGS. 9A and 10A show a state in which no rotational torque is transmitted from the first planetary gear 95 or the second planetary gear 96 to the torque transmission member 75 (transmitted gear 75b) (for example, the first planetary gear). 95 and the second planetary gear 96 are not engaged with the transmitted gear 75b).

  In this state, the clutch member 72 is engaged with the lock member 73 by the biasing force of the coil spring 74, that is, the meshing teeth 72a of the clutch member 72 and the meshing teeth 73a of the lock member 73 are meshed (see also FIG. 8).

  Accordingly, the clutch member 72 is in a locked state in which the rotation is restricted, and even if an external force is applied to the rotating shaft 71a (gear 71) to rotate, the rotating shaft 71a (gear 71) is engaged by the meshing teeth 72a and the engaging teeth 73a. ) Does not rotate. At this time, the boss 75a formed on the torque transmission member 75 is located at the intersection of the inclined surfaces 72d and 72d as shown in FIGS. 8, 9A, and 10A.

  From this state, when rotational torque is transmitted from the first planetary gear 95 or the second planetary gear 96 to the torque transmission member 75 (transmission gear 75b), the boss 75a hits the inclined surface 72d of the cam groove 72b, and the coil spring. The cam groove 72b (that is, the clutch member 72) is pushed upward against the urging force of 74.

  As a result, as shown in FIGS. 9B and 10B, the meshing teeth 72a of the clutch member 72 and the meshing teeth 73a of the lock member 73 are released, that is, the clutch member 72 is allowed to rotate. The lock is released. When the torque transmission member 75 continues to rotate, the boss 75a moves from the contact position with the inclined surface 72d of the cam groove 72b to the contact position with the side wall 72c. 75, the clutch member 72, and the rotating shaft 71a (gear 71) rotate integrally.

  In the operation of the locking means 70 described above, since the cam groove 72b is formed symmetrically, even if the transmitted gear 75b (torque transmission member 75) rotates in any direction, FIG. 9 (A) and FIG. If the locked state in FIG. 10 (A) is switched to the unlocked state in FIG. 9 (B) and FIG. 10 (B) and the transmitted gear 75b is stopped, the state in FIG. 9 (B) and FIG. Switching from the unlocked state to the locked state of FIG. 9 (A) and FIG. 10 (A).

  As described above, the lock unit 70 causes the clutch member 72 (the rotation shaft 71a and the gear 71) to rotate by the displacement of the boss 75a in the cam groove 72b in accordance with the switching of the rotation / stop of the torque transmission member 75. An allowed unlocking state and a locked state in which the rotation is locked are switched.

<< 4. Operation of gear device >>
Next, the overall operation of the gear device 8 including the first planetary gear 95 and the second planetary gear 96 will be described. In FIG. 2, the first planetary lever 77 has a boss 77 a on the side facing the side frame 61, and this boss 77 a is loosely inserted into an arcuate guide groove 62 formed in the side frame 61. The swingable range of the first planetary lever 77 is restricted by the guide groove 62.

  Similarly, the second planetary lever 78 has a boss 78 a on the side facing the side frame 61, and this boss 78 a is loosely inserted into an arcuate guide groove 63 formed in the side frame 61. The swingable range of the second planetary lever 78 is restricted by the guide groove 63.

  Here, the symbol γ1 indicates the swingable angle of the first planetary lever 77, and similarly the symbol γ2 indicates the swingable angle of the second planetary lever 78. As is apparent from the figure, in this embodiment, γ1 <γ2 is set, and the displacement amount when the first planetary gear 95 is displaced between the meshing position and the separated position is thereby determined as the second planetary gear. The displacement amount 96 is smaller than the displacement amount between the meshing position and the separation position.

  FIG. 2 shows a forward rotation state of the transport driving roller 35 (gear 90). In this state, the first planetary gear 95 rotates and drives the transmitted gear 75b of the locking means 70 in the direction of the arrow in FIG. The gear 71 rotates the gear 97, that is, the driving roller 32 in the direction of the arrow in the figure. That is, in this state, the recording paper P can be conveyed from the upstream side toward the downstream side.

  From this state, when the conveyance drive roller 35 (gear 90) is driven in reverse to perform the above-described skewing discharge type skew removal control, the first planetary gear 95 is moved from the transmitted gear 75b as shown in FIG. In this state, the transmission gear 75 is in a power cut state where it does not mesh with either the first planetary gear 95 or the second planetary gear 96.

  Accordingly, the lock means 70 is in a locked state in which the rotation shaft 71a (the gear 71) is locked so as not to rotate. At this time, the rotation of the driving roller 32 is locked by the locking means 70, but the downstream conveyance driving roller 35 is continuously driven in reverse, so that the recording paper P is placed between the driving roller 32 and the conveyance driving roller 35. And the leading end of the sheet is discharged to the upstream side of the transport driving roller 35, and the skew is removed.

  As described above, the rotation shaft 71b (gear 71, and hence the driving roller 32) by the lock means 70 is utilized by using the power cutting time in which neither the first planetary gear 95 nor the second planetary gear 96 meshes with the transmitted gear 75b. Is locked.

  When the transport driving roller 35 (gear 90) is switched to the normal rotation drive again from the state shown in FIG. 4, the amount of displacement until the first planetary gear 95 returns to the meshing position is set to be small. After the drive roller 35 is switched from the reverse rotation drive to the normal rotation drive, the normal rotation drive of the drive roller 32 can be quickly started without causing a large time lag.

  Accordingly, since the time during which the conveyance drive roller 35 rotates in the forward direction while the drive roller 32 is stopped can be shortened, the recording paper P is pulled between the drive roller 32 and the conveyance drive roller 35, and the drive roller 32 and the recording paper P It is possible to prevent the recording surface from being damaged due to slippage between the recording surface and the recording surface.

  Hereinafter, the operation and effect of the gear device 8 configured as described above will be described. When skewing control of the biting and discharging method is performed, the leading edge of the sheet is upstream of the transport drive roller 35 by the reverse drive of the transport drive roller 35. Vomited to the side. At this time, even if the discharged paper attempts to reverse the upstream drive roller 32, the drive roller 32 is securely locked. Accordingly, the sheet is reliably bent between the transport driving roller 35 and the driving roller 32, and the skew is reliably eliminated.

  That is, the drive roller 32 can be driven in either forward rotation or reverse rotation, and is reliably prevented from being locked (locked) when necessary. That is, the gear device 8 only allows one-way rotation of the rotation shaft. Unlike the one-way clutch, both forward / reverse bidirectional rotational driving and reliable reverse rotation prevention (rotation lock) when necessary can be satisfied.

  In addition, in a configuration in which a common drive source is used by the conveyance drive roller 35 and the drive roller 32, when performing skewing discharge-type skew removal control by both rollers, the conveyance drive roller 35 on the downstream side is reversed by a predetermined amount. The upstream drive roller 32 needs to be locked so as not to reverse in the meantime, but such a request can be met.

  Further, the first planetary gear 95 and the second planetary gear 96 are set to have different displacement amounts, and the first planetary gear 95 can be quickly displaced from the separated position to the meshing position. After the roller 35 is switched from the reverse rotation drive to the normal rotation drive, the normal rotation drive of the drive roller 32 can be started promptly without causing a large time lag, and the recording paper P can be prevented from being damaged.

<< 5. Operation and effect of auxiliary gear >>
Hereinafter, the auxiliary gear 98 included in the gear device 8 will be described in detail with reference to FIGS. 2 to 6 and other drawings as appropriate.
The gear device 8 includes an auxiliary gear 98 that meshes with the transmitted gear 75b and is capable of planetary movement around the transmitted gear 75b. More specifically, the side frame 61 is provided with a sub-frame 66 (not shown in FIGS. 2 to 5 and 6A: shown in FIG. 6B). An arcuate guide groove 65 centering on the rotation center of the transmitted gear 75b is formed. The rotating shaft 98a of the auxiliary gear 98 is loosely inserted into the guide groove 65, whereby the auxiliary gear 98 is supported so as to be capable of planetary movement around the transmitted gear 75b.

  When the drive gear 94 rotates in the first direction (counterclockwise direction in FIG. 2: when the conveyance drive roller 35 is driven to rotate forward), the auxiliary gear 98 has the same transmission gear 75b as shown in FIG. Since it rotates in the counterclockwise direction in the figure, it rotates together with the transmitted gear 75b at the position moved in the counterclockwise direction in the figure.

  From this state, in order to perform skewing discharge-type skew removal control, the rotation direction of the drive gear 94 is switched and rotated in the second direction (clockwise direction in FIG. 3: the conveyance drive roller 35 is driven in reverse. 3), the auxiliary gear 98 moves in the clockwise direction in FIG. 3 and engages with the first planetary gear 95.

  Here, when the first planetary gear 95 is switched from the forward rotation drive to the reverse rotation drive, the transmitted gear 75b is slightly reversed before the first planetary gear 95 is separated from the transmitted gear 75b as shown in FIG. Figure clockwise direction).

  At this time, the transmitted gear 75b attempts to move the first planetary gear 95 in the direction indicated by the reference numeral Fa, but this direction is opposite to the direction in which the first planetary gear 95 attempts to move away from the transmitted gear 75b. Contains a directional component. Therefore, as a result, even if the first planetary gear 95 tries to move away from the transmitted gear 75b (upper right direction in the figure), the teeth of the first planetary gear 95 are engaged with the teeth of the transmitted gear 75b, and the transmitted gear 75b There is a case where the first planetary gear 95 is held and the first planetary gear 95 cannot be separated from the transmitted gear 75b.

  However, in the gear device 8, as described above, the auxiliary gear 98 is engaged with the first planetary gear 95 and rotated in the counterclockwise direction in FIG. An attempt is made to move the first planetary gear 95 in the direction indicated by the symbol Fb. That is, since the first planetary gear 95 assists the operation of separating the first planetary gear 95 from the transmitted gear 75b, the first planetary gear 95 can be separated from the transmitted gear 75b.

  Further, when the first planetary gear 95 is going to be separated from the transmitted gear 75b, the transmitted gear 75b promotes the above-described retention for reasons other than the force received from the first planetary gear 95 (the clockwise direction in FIG. 5). ), The first planetary gear 95 becomes more difficult to separate. However, since the separating action by the auxiliary gear 98 acts on the first planetary gear 95, the first planetary gear 95 is surely separated from the transmitted gear 75b even if the transmitted gear 75b is rotated in the direction of promoting the above-mentioned retention. Can be made.

  Note that the case where the transmitted gear 75b is rotated in the clockwise direction in FIG. 5 for reasons other than the force received from the first planetary gear 95, for example, is not provided with the locking means 70, and FIGS. A case where the gear 71 and the transmitted gear 75b shown in FIG.

  That is, when the conveyance drive roller 35 is switched from the normal rotation drive to the reverse rotation drive in order to perform the biting discharge type skew removal control (FIG. 2 to FIG. 3), the paper P is strong, such as thick paper. Even when the conveyance drive roller 35 is driven in the reverse direction, the sheet P is not immediately bent between the upstream drive roller 32 and returned to the upstream side as it is, and as a result, the drive roller 32 may be rotated. .

  Then, as shown in FIG. 3, the gear 97 is rotated in the counterclockwise direction in FIG. 3, whereby the gear 71 meshing with the gear 97 is rotated in the clockwise direction in FIG. 3, and the transmitted gear 75b is also in the same figure. It will be turned clockwise. Therefore, the action of the transmitted gear 75b to retain the first planetary gear 95 is promoted.

  In this embodiment, since the lock means 70 is provided, the lock means 70 locks the gear 71 when the conveyance drive roller 35 is switched from normal rotation to reverse rotation. The rotation of the gear 71 is allowed by the action of rotating the transmitted gear 75b. This will be described in detail below.

  When the conveyance drive roller 35 is driven to rotate forward, the boss 75a of the torque transmission member 75 presses against the side wall of the cam groove 72b formed in the clutch member 72 as shown in FIG. Is pushed upward.

  When the conveyance drive roller 35 is driven in reverse from this state, the boss 75a temporarily moves to the left in FIG. 10B. As a result of the drive roller 32 being rotated by the paper P, the gear 97 is connected via the gear 97. As a result, the cam groove 72b moves to the left in FIG. 10B as well as the boss 75b. As a result, the clutch member 72 is not pushed downward in the figure, and the state shown in FIG. 10B is maintained, and a phenomenon that does not switch to the locked state occurs.

  As described above, even when the transport driving roller 35 is switched from forward rotation to reverse rotation, the gear 71 is rotated by the paper P and the transmitted gear 75b is rotated by the first planetary gear 95. As a result, the lock means 70 is locked. The rotation of the gear 71 is allowed without being switched to.

  However, since the gear device 8 includes the auxiliary gear 98 as described above, even if the transmitted gear 75b holds the first planetary gear 95 to be separated from the transmitted gear 75b, the first planetary gear 95 is connected to the transmitted gear. It can be reliably separated from 75b.

  In the present embodiment, the auxiliary gear 98 is restricted to some extent by the means for generating a resistance force in the displacement direction. 6A and 6B, reference numeral 99 denotes a friction member provided between the sub-frame 66 that pivotally supports the auxiliary gear 98 and the disk surface of the auxiliary gear 98. With the friction member 99, The auxiliary gear 98 is restricted so as not to move carelessly.

  This is due to the following reason. That is, as shown in FIG. 6A, the guide groove 65 that guides the rotating shaft 98a of the auxiliary gear 98 is inclined downward in the right direction in the figure, so that if there is no restriction, the auxiliary gear 98 is The gravitational force moves toward the first planetary gear 95, which may cause unintentional engagement with the first planetary gear 95, and may cause unnecessary collision noise between teeth.

  However, as described above, the friction member 99 generates a resistance force to the auxiliary gear 98 so that the auxiliary gear 98 does not move carelessly, so that the unintentional engagement with the first planetary gear 95 is not caused.

  The friction member 99 is arranged on the side farther from the transmission gear 75b than the rotation center of the auxiliary gear 98 in the direction of the straight line connecting the rotation center of the auxiliary gear 98 and the rotation center of the transmission gear 75b. A resistance force is applied to 98. As a result, the position (indicated by reference symbol Cp in FIG. 6 (A)) where a resistance force is applied to the auxiliary gear 98 in the rotational direction in which the engagement between the first planetary gear 95 and the auxiliary gear 98 should be avoided. Since the rotation moment around the center acts in the direction of moving the rotation shaft 98a away from the first planetary gear 95 as shown by the white arrow in FIG. 6A, the auxiliary gear 98 approaches the first planetary gear 95. It can be surely prevented.

FIG. 3 is a side sectional view showing a paper conveyance path of the printer according to the invention. The front view of the locking device concerning the present invention. The front view of the locking device concerning the present invention. The front view of the locking device concerning the present invention. The elements on larger scale around the first planetary gear. (A) is the elements on larger scale around the 1st planetary gear, (B) is a figure showing the attachment structure of auxiliary gear 98. The exploded perspective view of a locking means. The principal part expansion perspective view of a locking means. (A), (B) is sectional drawing of a locking means. (A), (B) is sectional drawing of a locking means.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Inkjet printer, 3 Feeding device, 4 Recording means, 5 Conveying means, 6 Ejecting means, 8 Gear device, 11 Paper cassette, 12 Separating member, 16 Pickup roller, 17 Oscillating member, 18 Oscillating shaft, 20 Driven roller , 21 Separating means, 22 Separating roller, 23 Driving roller, 25 First intermediate feeding unit, 26 Driving roller, 27 Assist roller, 29 Driven roller, 31 Second intermediate feeding unit, 32 Driving roller, 33 Assist roller, 35 Conveyance drive Roller, 36 transport driven roller, 37 on paper guide, 39 before paper guide, 40 carriage, 41 carriage guide shaft, 42 recording head, 44 discharge drive roller, 45 discharge driven roller, 46 reverse roller 47, 48 assist roller,
61 Side frame, 62, 63 Guide groove, 65 Guide groove, 66 Sub frame, 70 Locking means, 71 Gear, 71a Rotating shaft, 72 Clutch member, 72a Engagement tooth, 72b Cam groove, 72c Side wall, 72d Slope, 73 Lock member 73a meshing teeth, 73b hole, 74 coil spring, 75 torque transmission member, 75a boss, 75b transmission gear, 77 first planetary lever, 77a boss, 78 second planetary lever, 78a boss, 90 gear, 94 sun gear, 95 1st planetary gear, 96 2nd planetary gear, 97 gear, 98 auxiliary gear, 99 friction member, P recording paper

Claims (7)

A transmitted gear to which power is transmitted;
The drive gear is meshed with the drive gear so as to be capable of planetary movement, meshed with the transmitted gear when the drive gear rotates in the first direction, and from the transmitted gear when the drive gear rotates in the second direction. A power transmission gear that is spaced apart;
The drive gear meshes with the transmitted gear and can be moved in a planetary motion around the transmitted gear, and the power transmission gear is separated from the power transmission gear when the drive gear rotates in the first direction. The drive gear meshes with the power transmission gear as the drive gear is switched from the first direction rotation to the second direction rotation, and a force in a direction away from the transmitted gear is applied to the power transmission gear by the rotation. An auxiliary gear,
A gear device comprising: The gear device according to claim 1, wherein the auxiliary gear includes means for generating a resistance force in a direction in which the auxiliary gear moves toward the power transmission gear .
A gear device characterized by that. 3. The gear device according to claim 2, wherein the means for generating the resistance force is in a direction of a straight line connecting the rotation center of the auxiliary gear and the rotation center of the transmitted gear with respect to the rotation center of the auxiliary gear. And applying the resistance to the auxiliary gear on the side far from the transmitted gear,
A gear device characterized by that. 4. The gear device according to claim 1, wherein when the transmitted gear receives a rotational torque from the power transmission gear, a rotational torque is applied to a rotational shaft that receives the power from the transmitted gear accordingly. When the transmission of the rotational torque from the power transmission gear is cut off, a lock means is provided for locking the rotation shaft in response thereto.
A gear device characterized by that. The gear device according to claim 4, wherein the locking means rotates integrally with the rotary shaft and is displaceable in the axial direction of the rotary shaft;
A locking member provided in a fixed state that engages with the clutch member and restricts rotation of the clutch member;
A biasing member that biases the clutch member toward the lock member;
A torque transmission member that integrally includes the transmitted gear and includes a boss that is loosely inserted into a cam groove provided on an outer peripheral portion of the clutch member, and transmits rotational torque to the clutch member via the boss; Configured with
The boss is displaced in the cam groove in accordance with the switching of rotation / stop of the torque transmission member, so that the boss separates the clutch member from the lock member against the urging force of the urging member. An unlocked state and a locked state in which the boss allows displacement of the clutch member and engages the clutch member with the lock member are configured to be switched.
A gear device characterized by that. 6. The gear device according to claim 5, wherein the gear is meshed with the drive gear and provided around the drive gear in a planetary motion, and meshes with the transmitted gear when the drive gear rotates in the second direction. A second power transmission gear that rotationally drives the transmission gear in a direction opposite to the rotational driving direction of the power transmission gear and that is separated from the transmitted gear when the driving gear rotates in the first direction;
Using the power cutting time that is generated when the rotation direction of the drive gear is switched and the transmitted gear does not mesh with either the power transmission gear or the second power transmission gear, the lock shaft causes the rotation shaft to rotate. To lock,
A gear device characterized by that. Recording means for recording on a recording medium;
A first feed roller that is provided on the upstream side of the recording unit in a conveyance path of the recording medium and that conveys the recording medium to the recording unit;
A recording apparatus comprising: a second feeding roller that is provided on an upstream side of the first feeding roller in a conveyance path of the recording medium and that conveys the recording medium to the first feeding roller;
The first feed roller and the second feed roller are configured to be rotationally driven by a common drive motor,
The gear device according to any one of claims 4 to 6 is provided in a rotational torque transmission path from the first feed roller to the second feed roller, and the second locking mechanism includes the second gear. It is configured to be able to lock the rotation axis of the feed roller,
A recording apparatus.

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