JP2008095743A - Clutch device, recorded material feeding device and recording device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a clutch device wherein a lever member is not stroked by a shock when an engaging ratchet engages with a clutch engaging part of the lever member and becomes a clutch engaging state while a clutch member is in a rotation state even if the shock is great. <P>SOLUTION: The clutch device has the engaging ratchet 98, a toothing 94 capable of engaging with a driving side gear, the clutch member 93 capable of switching a clutch engaging state and a clutch disengaging state by rocking and the clutch engaging part 123 capable of engaging with the engaging ratchet 98 provided at a trigger lever 115 capable of rotating around a revolving supporting point and the trigger lever 115 for switching from the clutch engaging state to the clutch disengaging state by rocking the clutch member as the engaging ratchet engages with the clutch engaging part. An engagement holding means 160 is provided to prevent disengagement by a shock on engaging the engaging ratchet and the clutch engaging part. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to a clutch device mounted in various apparatuses including a recording device such as an inkjet recording device, a copying machine, and a facsimile, a recording material feeding device including the clutch device, and a recording device.

Patent Document 1 discloses a friction clutch including a one-rotation clutch member that turns on / off transmission of driving force to a paper feed roller and a swingable lever member (trigger lever) that determines whether the clutch member is on / off. And by swinging the clutch engaging portion of the lever member away from the engaging claw of the clutch member by reverse rotation of the drive motor of the paper feed roller, swinging in the direction approaching the clutch member by forward rotation, A clutch device is disclosed in which the clutch member is turned off and the paper feed roller is stopped when the paper feed roller rotates once.
JP 2001-341871 A

  In the clutch device disclosed in Patent Document 1, when the clutch member is in a rotating state and its engaging claw engages with the clutch engaging portion of the lever member and shifts to the “clutch engaged state”, the impact is generated. Is large, there is a problem that the lever member is repelled by the impact, and the engagement is disengaged and the clutch is disengaged.

  In particular, the cam mechanism for transmitting power from the drive side gear to the driven system has a structure in which a spring having a large spring coefficient is used and the drive side is changed to the driven side for a moment by the spring force and the clutch member is rotated quickly for a moment. If the friction force in the friction clutch mechanism is weak and the holding force at the time of occurrence of the impact is weak, the impact becomes large, and there is a problem that the clutch is likely to fall into the “clutch disengaged state”.

  The object of the present invention is that even when the clutch member is rotated and its engaging claw engages with the clutch engaging portion of the lever member and shifts to the “clutch engaged state”, even when the impact is large. An object of the present invention is to provide a clutch device that can hold the engaged state firmly without the lever member being bounced by the impact, a recording material feeding device including the clutch device, and a recording device. is there.

  In order to achieve the above object, a clutch device according to a first aspect of the present invention is a clutch device for turning on and off power transmission from a driving gear rotated by a driving motor to a driven system. And an engaging claw and a tooth portion engageable with the drive side gear, and can swing around a swing fulcrum, and by swinging, the tooth portion and the drive side gear A clutch member that can be switched between a clutch engagement state and a clutch non-engagement state, and a clutch member that is constantly biased by the clutch biasing means to swing to the clutch engagement state side, and a rotation fulcrum An arm that is pivotable about the center, and a clutch engaging portion that is provided on the arm and is engageable with the engaging claw, wherein the engaging claw is engaged with the clutch while the clutch member and the driven system are rotating. By engaging the engaging part, A lever member that swings the clutch member to switch from the clutch engagement state to the clutch non-engagement state, and is disengaged by an impact when the engagement claw and the clutch engagement portion are engaged. It is characterized by comprising engagement holding means for preventing this.

  According to the present invention, since the engagement claw and the clutch engagement portion are engaged, the engagement holding means for preventing the engagement from being disengaged due to the impact is provided. When the engaging claw engages with the clutch engaging portion of the lever member and shifts to the “clutch engaged state”, even when the impact is large, the lever member may be repelled by the impact. The engagement state can be held firmly.

In the clutch device according to a second aspect of the present invention, in the first aspect, the engagement holding means is provided on at least one of an engagement surface of the engagement claw and an engagement surface of the clutch engagement portion. It is a high friction member made.
According to the present invention, the high friction member maintains the contact state between the engagement surface of the engagement claw and the engagement surface of the clutch engagement portion. The engagement state can be firmly held by the friction member.

  The clutch device according to a third aspect of the present invention is characterized in that, in the second aspect, the high friction member is a rubber material or a cork material. Thereby, the said effect can be obtained at low cost. Further, since the impact can be absorbed by the elastic force, the engaged state can be held more firmly.

  The clutch device according to a fourth aspect of the present invention is characterized in that, in the first aspect, the engagement holding means is configured by using a material of the lever member as a high friction material. It is. Also by this structure, the same effect as the first aspect can be obtained. As the material of the high friction material, a rubber material or a cork material is preferable.

  A clutch device according to a fifth aspect of the present invention is the clutch device according to the first aspect, wherein the engagement holding means is capable of waiting and moving to a position near the clutch member in the swinging direction of the lever member. The movable member provided is placed in a standby position at the vicinity to restrict the swing of the lever. Also by this structure, the same effect as the first aspect can be obtained.

Further, the sixth aspect of the present invention provides a drive motor, a clutch device for turning on / off power transmission from a drive-side gear rotated by the drive motor to a driven system, and a recording material. A recording material feeding device comprising: a feeding roller shaft belonging to the driven system that is rotated by power being transmitted from the driving-side gear and is rotated; The clutch device according to any one of the first to fifth aspects.
According to the present invention, in the recording material feeding device such as a paper feeding device, it is possible to obtain the same functions and effects as those of the first to fifth aspects. A recording apparatus comprising: a recording material feeding device; and a recording execution unit that executes recording on the recording material fed from the recording material feeding device, wherein the recording material feeding device is It is a recording material feeding device according to the sixth aspect.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings. FIG. 1 is a perspective view from the lower front side of a recording material feeding device of an ink jet printer to which the recording material feeding device according to the present invention can be applied, and FIG. 2 is a rear perspective view of the hopper when the medium return lever is up. 3 is a rear perspective view of the hopper when the medium return lever is down, FIG. 4 is a right side view of the recording material feeding device, and FIG. 5 is an enlarged perspective view around the hopper operating member. 6 to 9 are diagrams showing the relationship between the rotational position of the camshaft and the medium return lever in stages, FIG. 10 is a side view showing the state when the hopper is reset, and FIG. 11 is the state when the hopper is up. FIG.

  12 is a side view showing a drive transmission system mounted on the feeding device, FIG. 13 is a perspective view showing the drive transmission system, FIG. 14 is an exploded perspective view of the drive transmission system, and FIG. FIG. 16 is an explanatory view showing a state when the engaging claw and the clutch engaging portion are engaged, and FIG. An explanatory view (a) showing the start of the transition to the clutch engaged state is accompanied by an enlarged sectional view (b) of the main part, and FIG. 18 is an explanatory view showing a state where the tooth portion collides with the gear teeth of the ratchet wheel. FIG. 19A is an enlarged sectional view (b) of a main part, FIG. 19 is an explanatory view (a) showing a clutch engaged state, and an enlarged sectional view (b) of a main part is also shown. An explanatory view (a) showing the start of raising of the trigger lever is accompanied by an enlarged sectional view (b) of a main part, and FIG. 21 shows raising of the trigger lever. FIG. 22 is an explanatory diagram (a) illustrating the state of completion and an enlarged cross-sectional view (b) of the main part, and FIG. 22 is an explanatory diagram (a) illustrating the state immediately before the engagement of the engagement claw and the clutch engagement part. FIG. 23 is an explanatory view showing a state in which the tooth portion is engaged with the gear tooth of the ratchet wheel, and FIG. 24 is a diagram showing the rotation locus of the tooth portion across the gear tooth. FIG. 25 is an explanatory view showing a state where the tooth portion is separated from the gear teeth of the ratchet wheel, and FIG. 26 is an explanatory view (a) showing a state where the state is shifted to the clutch non-engagement state. FIG. 27B is also shown, and FIG. 27 is a perspective view of the friction clutch mechanism.

  A recording material feeding apparatus 1 shown in FIG. 1 is a liquid ejecting apparatus that ejects liquid onto a recording apparatus such as an ink jet printer that performs recording on a relatively small recording material such as a postcard or a business card, or a relatively small ejection medium. Compared with a feeding device for a recording apparatus used in a normal office such as a Japanese Industrial Standard A4 or B5 version, it is a small size as a whole. Since the feeding device for the liquid ejecting apparatus has substantially the same structure as the feeding device for the recording apparatus, the following description will focus on the feeding apparatus for the recording apparatus.

  The recording material feeding apparatus 1 has a feeding tray 3 that can hold a plurality of recording materials P in a stacked state, and the lower end side of the recording material feeding device 1 can swing around an upper oscillating fulcrum 2a. A hopper 2 is provided, and a feed roller 5 is rotatably supported on a feed roller shaft 4 provided immediately above the feed tray 3.

  A separation pad 7 is provided at a position facing the feeding roller 5. That is, the recording material P is nipped and held by the feeding roller 5 and the hopper 2, and the recording material P is picked up from the feeding tray 3 by rotating the feeding roller 5 in this state. When two or more recording materials P on the tray 3 are about to be fed out (this state is hereinafter referred to as “double feeding”), only the uppermost recording material P is downstream in the feeding direction, that is, A separation pad 7 is provided as separation means for separating from other recording materials so as to advance forward. The separation pad 7 is formed of an elastic material such as an elastomer, and microscopically, the leading end of the recording material P moves downstream while being slightly sunk into the pad surface.

  In addition, a medium return lever 9 is provided in the vicinity of the downstream side of the hopper 2 for returning the recording material P other than the uppermost portion fed to the feeding tray 3 to the feeding tray 3. The hopper 2 and the medium return lever 9 are operated via the same drive system. That is, the hopper 2 has a drive transmission system 11, a camshaft 13 that branches the power transmitted through the drive transmission system 11 to the hopper 2 and the medium return lever 9, and a hopper that transmits driving from the camshaft 13 to the hopper 2. It operates via the operating member 15 (FIG. 2). On the other hand, the medium return lever 9 operates via the drive transmission system 11, the cam shaft 13, the cam transmission return member 16, and the return action member 17 (FIG. 2). Since the medium return lever 9 rotates while contacting the back surface of the recording material to be conveyed as described later, it is preferable that the frictional resistance is as small as possible, and the sliding resistance of polyacetal resin or the like is small. It is desirable to form with a raw material. Hereinafter, these configurations will be described in detail.

  The drive transmission system 11 includes a drive motor 19 and a plurality of gears 21 that mesh with an output pinion of the drive motor 19. The last gear 21 a of the drive transmission system 11 meshes with a cam shaft gear 41 formed at the end of the cam shaft 13. A first cam 43 (FIG. 2) is formed in the vicinity of the cam transmission return member 16 on the cam shaft 13, and a second cam 45 (FIG. 1) is formed in the vicinity of the return action member 17. The driving force of the drive motor 19 is transmitted to the medium return lever 9 and the hopper 2 through the first cam 43 and the second cam 45, respectively.

  As shown in FIGS. 2, 3 and 5, the hopper actuating member 15 is rotatably supported with respect to the base frame 47, and from the rotating shaft 50 portion (FIGS. 2 and 3). A hopper pressing portion 49 and a cam receiving portion 51 (FIGS. 3 and 5) are formed. Further, a torsion spring 53 is provided on the rotating shaft 50 portion of the hopper actuating member 15, one end of the torsion spring 53 is fixed to the base frame 47, and the other end is locked to the hopper pressing portion 49. A hopper action end 55 is formed at the end of the hopper pressing portion 49, and the hopper action end 55 is in contact with the lower surface side of the hopper 2. The other end of the torsion spring 53 is engaged with the hopper pressing portion 49, so that the hopper action end 55 urges the hopper 2 to always rise.

  The second cam 45 of the cam shaft 13 is in contact with the second cam receiving portion 51 of the hopper operating member 15 so as to operate as a cam follower. The cam action of the second cam 45 rotates the hopper operating member 15. By rotating around the shaft 50, the hopper pressing portion 49 is retracted to the lower side of the hopper 2 at a predetermined timing, and the hopper 2 is moved downward by its own weight by releasing the pressing from the lower side of the hopper 2. It is designed to rotate.

  Next, as shown in FIGS. 2 and 3, the cam transmission return member 16 has a substantially cylindrical shape as a whole, and a first cam receiving portion 57, a spring locking portion 59, and the like are provided on the circumferential surface of the column. Is formed. The cam transmission return member 16 is rotatable around the axis line on an axis (not shown) provided on the base frame 47 so that one end side of the cylinder axis is parallel to the feed roller axis 4. Is attached. Further, two guide plates 61 are formed at the other end portion of the cam transmission return member 16, and a guide gap 63 is formed between the two guide plates 61. The first cam receiving portion 57 cooperates with the first cam 43 of the cam shaft 13 to perform a cam action, and the other end of the coil spring 65 whose one end is fixed to the base frame 47 is engaged with the spring locking portion 59. It has stopped.

  As shown in FIGS. 2, 3, and 5, the return action member 17 is formed in a U shape so as to straddle the shaft portion 67 formed on the cam transmission return member 16 side and the hopper operation member 15. Lever base 69 and a shaft end 68 projecting from the lever base 69 opposite to the shaft 67. The shaft end 68 is pivotally supported by a long hole-shaped bearing portion 48 provided in the base frame 47 so as to be movable in a direction retreating from the return operation region by the medium return lever 9. A slide plate 70 is integrally formed at the end of the shaft portion 67, and the slide plate 70 is slidable in a direction perpendicular to the axis of the shaft portion 67 between the guide gaps 63 of the cam transmission return member 16. Is inserted.

  One end of each torsion spring 71 is engaged with both outer portions of the U-shaped lever base 69, and the other end of each torsion spring 71 is fixed and engaged with the base frame 47. The lever base 69 receives an urging force from the torsion spring 71 in the forward direction (direction in which the recording material being fed is pushed up from the back surface) opposite to the reverse direction. The shaft end 68 is always pressed against the front end of the bearing portion 48 by this forward biasing force. The medium return lever 9 is formed at both ends of the U-shape of the lever base 69 as described above.

  That is, when the medium return lever 9 is rotated, the return acting member 17 returns the recording material P having its tip 10 double fed to the separation pad 7 to the feeding tray 3 during the operation of returning the torsion spring 71. The urging force receives a force in the forward direction, while the tip 10 is pressed against the back surface of the uppermost recording material P and receives a force that is pushed back against the force in the forward direction. Therefore, in a state in which the cam guide surface 77 described later is not provided, the tip 10 of the medium return lever 9 takes a simple arc-shaped locus at the beginning of rotation, and the tip 10 comes into contact with the back surface of the recording material P. After that, a turning locus in which both the forces are balanced is taken.

  In this embodiment, the posture of the recording material being fed is determined by the auxiliary roller 6 that determines the posture so that the recording material does not contact the feeding roller 5. The tip 10 of the medium return lever 9 comes into contact with the back surface of the recording material at a position close to the contact point with the auxiliary roller 6 in the rotation locus. In this structure, when the recording material has high rigidity, the recording material is difficult to bend, and therefore, when the medium return lever 9 is pushed back, a scratch mark may remain on the back surface of the recording material. Further, in the mounting structure of the medium return lever 9, since the push-back phase angle is almost horizontal, contribution of gravity cannot be expected, and the medium return lever 9 is more difficult to be pushed back due to the twisting resistance of the bearing portion. Scratches are likely to remain. Or there is a possibility that it may lead to a problem of step-out of the drive motor 10.

  In order to solve this problem, as shown in FIG. 6, in the present invention, a cam guided portion 73 is formed on the outer surface of each medium return lever 9, while the medium return lever 9 is a hopper. A cam guide surface 77 for guiding the cam guided portion 73 is formed in a notch 75 (FIG. 1) formed in a corresponding portion of the base frame 47 so as to protrude to the upper surface side of 2. . The above-described torsion spring 71 urges the lever base 69 toward the cam guide surface 77. As a result, the cam guided portion 73 is always urged so as to be in contact with and guided by the cam guide surface 77. Accordingly, the medium return lever 9 is constantly urged in a direction protruding upward from the upper surface of the hopper 2, and the protruding position is restricted by the cam guide surface 77.

  Here, the operation of the hopper 2 and the medium return lever 9 will be described with reference to FIGS. 2, 3 and 6 to 11. First, as shown in FIGS. 2 and 6, when the medium return lever 9 is in the up state, that is, before the recording material P is fed, the second cam 45 of the camshaft 13 is the second cam of the hopper actuating member 15. By the cam action with the receiving portion 51, the hopper pressing portion 49 is retracted below the hopper 2 (FIG. 10), and the hopper 2 is lowered by its own weight by releasing the pressing from the lower side of the hopper 2. It is in the state rotated to. At this time, the recording material P on the feeding tray 3 is not in contact with the feeding roller 5. Further, the first cam 43 of the cam shaft 13 cams on the first cam receiving portion 57, so that the cam transmission return member 16 is rotated against the spring pulling action of the coil spring 65, and the lever base 69 is moved accordingly. By rotating, the front end 10 of the medium return lever 9 protrudes upward from the notch 75.

  As shown in FIG. 7, when the cam shaft 13 rotates and the first cam 43 is disengaged from the first cam receiving portion 57, the tip 10 of the medium return lever 9 is retracted downward by the spring pulling force of the coil spring 65 (FIG. 3). reference). When the cam shaft 13 rotates to the position shown in FIG. 8, the second cam 45 of the cam shaft 13 is disengaged from the second cam receiving portion 51 of the hopper operating member 15, and the hopper pressing portion 49 is moved to the hopper by the action of the torsion spring 53. Since the lower surface side of 2 is pressed upward (FIG. 11), the hopper 2 rises. As a result, the uppermost recording material P on the feeding tray 3 comes into contact with the feeding roller 5 and feeding by the rotation of the feeding tray 3 is started.

  When the cam shaft 13 rotates to the position shown in FIG. 9, the first cam 43 of the cam shaft 13 starts to engage with the first cam receiving portion 57 again. While the cam shaft 13 rotates from the position shown in FIG. 9 to the position shown in FIG. 6, the shaft portion 67 and the lever base portion 69 rotate together via the cam transmission return member 16. At this time, since the cam guided portion 73 is guided by the cam guide surface 77, the position of the axis line connecting the shaft portion 67 and the shaft end 68 (same as the axis line of the shaft portion 67) retreats, and accordingly, the medium return lever 9 The trajectory of the tip 10 passes below the trajectory when the cam guided portion 73 and the cam guide surface 77 are not provided. The shape of the cam guide surface 77 is set so that this locus is the same as the locus in which the tip 10 of the medium return lever 9 moves along the shape of the back surface of the recording material P being fed.

  That is, the tip 10 of the medium return lever 9 contacts the back surface of the recording material at a position far from the contact point with the auxiliary roller 6. Since the recording material easily bends even if it has the same rigidity as the distance increases, there is little possibility that a scratch mark will remain on the back surface of the recording material when the medium return lever 9 is pushed back. In addition, since the pushing-back phase angle rises larger than the horizontal, it is possible to expect the contribution of gravity, and there is little risk of the bearing portion being twisted, and the medium returning lever 9 is more easily pushed back, and the scratch marks are less likely to remain. Furthermore, the possibility of leading to the problem of step-out of the drive motor 10 is reduced.

  As described above, the cam guided portion 73 is guided by the cam guide surface 77, and the medium return lever 9 moves in the direction of a straight line connecting the tip 10 of the medium return lever 9 and the rotation fulcrum of the medium return lever 9. While moving backward, the tip 10 of the medium return lever 9 rotates along the locus along the posture of the back surface of the recording material P being fed. Therefore, an excessive load or excessive frictional force that occurs when the front end 10 of the medium return lever 9 passes through the back surface of the recording material P being fed does not occur. Problems such as scratches on the back surface and step-out of the drive motor 19 due to the load can be solved.

  Next, the drive transmission system 11 to the feeding roller 5 and the camshaft 13 will be described with reference to FIGS. A first gear 83 (gear 21 in FIG. 1) meshes with the output pinion 81 of the drive motor 19, and the hopper 2 is automatically fed via a second gear 85 that is a composite gear with the first gear 83. The driving force is transmitted to the mechanism, and similarly, the driving force is transmitted to the ink suction pump via the first gear 83 and the third gear 87 that is a composite gear.

  The second gear 85 meshes with the fourth gear 89, and the fourth gear 89 meshes with the fifth gear 91 and the eighth gear 111. The fifth gear 91 has a claw wheel 92 (FIG. 14) that is formed integrally with the fifth gear 91 and corresponds to the drive side gear. The origin of the claw wheel 92 is 10 teeth with a diameter of 7.5 mm. Yes, pretty small. The fifth gear 91 and the claw wheel 92 are freely rotatable with respect to the feeding shaft 78 of the feeding roller 5, and the tooth portion 94 formed inside the clutch member 93 is engaged with the claw wheel 92. For the first time, the driving force is transmitted to the feeding shaft 78 of the feeding roller 5.

  That is, the clutch member 93 is rotatable about the swing fulcrum 96, and the clutch member 93 is connected to the clutch auxiliary member 97 at the swing fulcrum 96 so as to be rotatable relative to each other. A torsion coil spring 95 is provided between the clutch member 93 and the clutch auxiliary member 97, and the action of the clutch member 93 is always biased in a direction in which the tooth portion 94 engages with the gear tooth 79 of the ratchet wheel 92. ing. The clutch auxiliary member 97 is fixed to the feed shaft 78 of the feed roller 5, so that the driving force is transmitted to the feed shaft 78 when the tooth portion 94 engages with the claw wheel 92. An engaging claw 98 is formed on the outer peripheral side of the clutch member 93.

  The feed shaft 78 of the feed roller 5 is provided with a sixth gear 99 that constitutes a driven system gear, and the seventh gear 101, the gear 21a, and the camshaft gear 41 are sequentially provided in the sixth gear 99. The gear train is constituted by meshing. The drive transmission system after the camshaft gear 41 is as described above (FIGS. 1 to 11).

  In the present embodiment, as shown in FIG. 15B, the eighth gear 111 meshed with the fourth gear 89 is formed with an engaging convex portion 100 formed in an arc shape over 90 °. It is connected to the trigger lever 115 side through a differential gear described later. The trigger lever 115 corresponds to a lever member and can be rotated around the lever shaft 113, and includes an arm 116, a driven differential gear 119 formed around the lever shaft 113, and a friction clutch mechanism 121. Yes. A clutch engagement portion 123 that extends toward the clutch member 93 and can be engaged with the engagement claw 98 is formed at the tip of the arm 116. Further, the engaging claws 98 and the clutch engaging portion 123 are formed with engaging surfaces 125 and 127 (FIG. 14) that come into contact with each other when engaged.

  In this embodiment, the driven differential gear 119 is formed with an engaged convex portion 129 extending over 170 °, and the engaged convex portion 129 is engaged with the end portion of the engaging convex portion 100 described above. When this is done, the rotational driving force is transmitted to the engaged convex portion 129. Further, when the engaging convex portion 100 is moving in the non-transmitting portion 131 where the engaged convex portion 129 of the driven differential gear 119 is not formed, the driving force is not transmitted to the driven differential gear 119. As described above, the engaging convex portion 100 and the engaged convex portion 129 constitute a differential gear.

  As shown in FIG. 27, the friction clutch mechanism 121 includes an annular portion 135 formed with a slight gap around the cylindrical base portion 133 of the driven differential gear 119, a storage portion 137 for storing the compression spring 117, and a storage portion. At the boundary between the portion 137 and the annular portion 135, a sliding contact piece 139 is provided that can be elastically deformed toward the cylindrical base 133 by the elastic force of the compression spring 117. The sliding contact piece 139 is pressed against the surface of the cylindrical base portion 133 by the elastic force of the compression spring 117, so that when the driven differential gear 119 rotates, the sliding movement of the trigger lever 115 is not restricted from the outside. The trigger lever 115 is also rotated together by the frictional force between the contact piece 139 and the cylindrical base 133.

  Next, switching between the clutch engaged state and the clutch non-engaged state by the operation of the clutch member 93 will be described with reference to FIGS. 15 to 26. In this specification, the “clutch engaged state” means a state in which the teeth 94 of the clutch member 93 are engaged with the gear teeth 79 of the claw wheel 92, and the “clutch disengaged state” means the teeth of the clutch member 93. The state in which the portion 94 is disengaged from the gear teeth 79 of the claw wheel 92 is said.

  First, the transition to the clutch non-engagement state will be described. As shown in FIG. 21, when the drive motor 19 is rotating forward, the fourth gear 89 rotates in the direction of the arrow in FIG. 21 (a), and this driving force is transmitted to the fifth gear 91 and the claw wheel 92, A driving force for rotating the trigger lever 115 toward the clutch member 93 is transmitted via the eighth gear 111. Then, after the clutch member 93 rotates clockwise to reach the state shown in FIG. 22A, the clutch member 93 further rotates clockwise and the engagement claw 98 engages with the clutch engagement portion 123. Accordingly, the clutch member 93 swings in the counterclockwise direction of FIG. 15A at the swing support point 96 against the pulling force of the torsion coil spring 95. As a result, the tooth portion 94 of the clutch member 93 is disengaged from the gear tooth 79 of the ratchet wheel 92 and the clutch is disengaged.

  When the clutch engaging portion 123 engages with the engaging claw 98, as shown in FIG. 16, the clutch engaging portion 123 pushes the engaging claw 98 in the direction indicated by the arrow 143, and the tooth portion 94 of the clutch member 93 is The clutch member 93 is swung so as to be completely separated from the gear teeth 79 of the claw wheel 92 with a clearance. Therefore, as shown in FIG. 16, the rotation locus 141 of the clutch engaging portion 123 overlaps with the engaging claw 98. By adopting such a configuration, it is possible to prevent the tooth portion 94 of the clutch member 93 from colliding with the gear tooth 79 of the claw wheel 92 and generating a ticking sound.

  As described above, the operation in which the clutch engagement portion 123 pushes the engagement claw 98 in the direction indicated by the arrow 143 depends on the formation angle of the engagement surface 125 of the engagement claw 98 and the engagement surface 127 of the clutch engagement portion 123. Is also defined. Therefore, the engagement surfaces 125 and 127 are engaged with each other at such an angle that the clutch member 93 swings so that the tooth portion 94 of the clutch member 93 is completely separated from the gear tooth 79 of the claw wheel 92 with a clearance. It comes to match.

  Next, the transition to the clutch engaged state will be described. When the drive motor 19 rotates in the reverse direction from the state shown in FIG. 15, the eighth gear 111 rotates until the first end 145 of the engaging convex portion 100 contacts the engaged convex portion 129 as shown in FIG. 17B. . After the first end 145 of the engaging convex portion 100 contacts the engaged convex portion 129, the driven differential gear 119 rotates to cause the trigger lever 115 to start rotating counterclockwise, thereby triggering The lever 115 rotates to the position shown in FIG. As a result, the engagement of the clutch engaging portion 123 with the engaging claw 98 is released, and therefore the clutch member 93 is swung around the swinging fulcrum 96 by the biasing force of the torsion coil spring 95 so that the tooth portion 94 is moved to the claw wheel. Try to engage 92.

  However, as shown in FIG. 18, the tooth portion 94 of the clutch member 93 may collide with the tip of the gear tooth 79 of the claw wheel 92, and the tooth portion 94 may not engage with the gear tooth 79. Therefore, by rotating the drive motor 19 in the forward direction, the ratchet wheel 92 is rotated by one gear tooth in the clockwise direction of FIG. 19A, and the tooth portion 94 is reliably engaged with the gear tooth 79. Due to the forward rotation of the drive motor 19, the eighth gear 111 rotates in the clockwise direction in FIG. 19B. However, since the engaging convex portion 100 passes through the non-transmitting portion 131, the rotational driving force is generated during this period. 115 is not transmitted.

  In the present embodiment, the differential angle from the state of FIG. 17B to the state of FIG. 15B is 100 °, and the rotation angle for rotating by one gear tooth is 67.5. Therefore, there is a margin of 32.5 ° before the driving force is transmitted to the trigger lever 115 at the time of FIG. Thus, since the trigger lever 115 is not rotated by the differential gear when the drive motor 19 is rotating forward, the clutch engaging portion 123 is not re-engaged with the engaging claw 98.

  As shown in FIG. 19A, when the tooth portion 94 is engaged with the gear tooth 79, the clutch is engaged, and the clutch member 93 starts rotating. When the engaging convex portion 100 is rotated by the remaining 32.5 ° and the second end 147 of the engaging convex portion comes into contact with the engaged convex portion 129 (see FIG. 20B), the trigger lever 115 is As shown in FIG. 21A, the clutch member 93 is again rotated toward the clutch member 93. At this time, since the engaging claw 98 is rotated upward, the clutch engaging portion 123 is not engaged with the engaging claw 98. Incidentally, in the state shown in FIG. 21A, the hopper pressing portion 49 starts to rotate due to the cam action of the second cam 45 and enters the feeding operation.

  When the clutch member 93 is rotated almost once and the engaging claw 98 is immediately before the clutch engaging portion 123 is engaged, the second cam follower 51 is placed on the top portion 149 of the second cam 45 as shown in FIG. It becomes a state to reach. When the second cam follower 51 exceeds the top portion 149 of the second cam 45, the second cam follower 51 actively slides down the cam inclined surface 151 according to the profile of the second cam 45 due to the biasing force of the torsion spring 53 and fits into the recess 153. To do. At that time, the engaging claw 98 is not yet engaged with the clutch engaging portion 123.

  When the second cam follower 51 actively slides down the cam slope 151, the cam shaft 13 is also actively moved, and the cam shaft 13 side is changed from the driven position to the driving side. The clutch member 93 is swung by the driving force at this time so that the engaging claw 98 is engaged with the clutch engaging portion 123 and the clutch member 93 is actively moved. This causes a state (reference numeral 155) that the tooth portion 94 of the toothed wheel 94 is separated from the gear tooth 79 of the claw wheel 92. Since the engaging claw 98 engages with the clutch engaging portion 123 in this separated state, the teeth 94 of the clutch member 93 are clawed as shown in FIG. The gear 92 of the vehicle 92 can be instantaneously and without resistance and can enter the clutch non-engagement state.

23 and 24 show a state where the tooth portion 94 of the clutch member 93 is engaged with the gear tooth 79 of the claw wheel 92 to transmit power. In such a state, it is necessary to prevent the tooth portion 94 of the clutch member 93 from being disengaged from the gear tooth 79 of the claw wheel 92 and causing tooth skipping. Therefore, in a state in which the cam follower 51 is not fitted in the recess 153, as shown in FIG. 24, at least a part of the tooth portion 94 of the clutch member 93 when the clutch member 93 is about to shift to the clutch non-engagement state (this example) Then, the tooth portion 94 and the gear tooth 79 of the claw wheel 92 are formed so that the rotation locus 157 of the tip portion 156) of the tooth portion 94 on the gear tooth 79 side crosses the shape of the gear tooth 79 of the claw wheel 92. .
That is, in FIG. 24, in order for the tooth portion 94 to release the engagement with the gear tooth 79, the tip end portion 156 must rotate along the rotation locus 157. Therefore, the tooth portion 94 cannot be disengaged from the gear teeth 79 unless the hook wheel 92 rotates in the reverse direction.

  Therefore, when the tooth portion 94 engages with the gear tooth 79 and transmits power, there is almost no possibility that the engagement between the tooth portion 94 and the gear tooth 79 is released, and tooth skipping does not occur. On the other hand, when shifting to the clutch non-engagement state, as shown in FIG. 25, the tooth portion 94 is easily separated from the gear tooth 79, and therefore, the rotation locus 157 becomes the gear tooth as shown in FIG. Even if the configuration across 79 is employed, the state in which the tooth portion 94 does not come off the gear tooth 79 does not occur.

  Next, FIG. 28 shows a moment when the engaging claw 98 of the clutch member 93 is engaged with the clutch engaging portion 123 of the trigger lever 115 which is a lever member. In this embodiment, there is provided engagement holding means for preventing the engagement state from being released due to an impact when the engagement claw 98 and the clutch engagement portion 123 are engaged. The engagement holding means includes a high friction member 160 attached to the engagement surface 127 of the clutch engagement portion 123. Specific examples of the high friction member 160 include a rubber material or a cork material.

  It should be noted that the engagement surface 127 of the clutch engaging portion to which the high friction member 160 is attached and the engagement surface 125 of the clutch member have a relationship as shown in FIG. 16 (the rotation locus of the clutch engaging portion 123). 141 does not have to be configured in such a manner as to overlap with the engaging claw 98 of the clutch member, but it is better if they overlap in this manner.

According to the present embodiment, when the engaging pawl 98 and the clutch engaging portion 123 are engaged, that is, when the clutch member 93 is rotating, the engaging pawl 98 is engaged with the clutch engaging portion 1213 of the trigger lever 115. When the transition to the “clutch engaged state” is made, even if the impact at that time is large, the high friction member 160 as the engagement holding means is provided. The engagement state between the engagement claw 98 and the clutch engagement portion 123, that is, the contact state between the engagement surface 125 of the engagement claw 98 and the engagement surface 127 of the clutch engagement portion 123 is firmly held without being broken. can do.
In the present embodiment, since the high friction member 160 is a rubber material or a cork material, the impact can be absorbed by the elastic force of the material itself, and the engaged state can be held more firmly.

  In particular, as shown in FIG. 22, the second cam follower 51 actively slides down the cam inclined surface 151 based on the biasing force of the torsion spring 53, so that the cam shaft 13 is also actively moved and the cam shaft 13 side is driven. When the structure changes from the stand to the driving side, the clutch member 93 swings with the instantaneous driving force at this time, and the engaging claw 98 engages with the clutch engaging portion 123, the impact becomes large. Further, when the frictional force in the friction clutch mechanism 121 is weak and the holding force at the time of the occurrence of the impact is weak, the impact becomes large, so that there is a problem that the clutch is likely to fall into a “clutch disengaged state”. The structure provided with the high-friction member 160 according to the present embodiment provides a more remarkable effect when applied to a structure that easily falls into a “clutch disengaged state” due to an impact.

  FIG. 29 also shows the moment when the engaging claw 98 of the clutch member 93 is engaged with the clutch engaging portion 123 of the trigger lever 115 which is a lever member. In the present embodiment, the high friction member 161 as the engagement holding means is attached to the engagement surface 125 of the engagement claw 98 of the trigger lever 115. Specific examples of the high friction member 160 include a rubber material or a cork material. The same effect as the structure of FIG. 28 is obtained.

  The engagement holding means may be configured by using a material of the trigger lever 115 itself as a high friction material such as a rubber material or a cork material. Similar effects can be obtained by this structure.

  FIG. 30 shows that the engagement holding means waits at a position near the carriage 170 that is a movable member that is provided in a position near the opposite side of the clutch member 93 in the swing direction of the trigger lever 115 so as to be movable. Thus, it can be realized also by a configuration that regulates the swing of the trigger lever 115. In the figure, reference numeral 171 indicates a known guide shaft for moving the carriage 170.

  As described above, the embodiment in which the present invention is applied to the ink jet recording apparatus has been described. However, the present invention can also be applied to a liquid ejecting apparatus including a feeding device that feeds a material to be ejected.

1 is a perspective view from below of a front side of a feeding device of an inkjet printer to which the present invention is applicable. The rear perspective view of a hopper at the time of a medium return lever up. The rear perspective view of a hopper at the time of a medium return lever down. The right view of a feeder. FIG. 3 is an enlarged perspective view around a hopper operating member. The figure which shows the relationship between the rotation position of a cam shaft, and a medium return lever in steps. The figure which shows the relationship between the rotation position of a cam shaft, and a medium return lever in steps. The figure which shows the relationship between the rotation position of a cam shaft, and a medium return lever in steps. The figure which shows the relationship between the rotation position of a cam shaft, and a medium return lever in steps. The side view which shows the state at the time of a hopper reset. The side view which shows the state at the time of a hopper up. The side view which shows the drive transmission system mounted in the feeding apparatus. The perspective view which shows the drive transmission system. The exploded perspective view of the drive transmission system. An explanatory view (a) showing a clutch non-engagement state is shown together with an enlarged sectional view (b) of a main part. Explanatory drawing which shows the state at the time of engagement of an engaging claw and a clutch engaging part. The main part enlarged sectional view (b) is shown together in the explanatory view (a) showing the start of the transition to the clutch engaged state. An explanatory view (a) showing a state in which the tooth portion collides with the gear teeth of the claw wheel is shown together with an enlarged sectional view (b) of a main part. An explanatory view (a) showing a clutch engagement state is shown together with an enlarged sectional view (b) of a main part. An explanatory view (a) showing the start of raising the trigger lever is shown together with an enlarged sectional view (b) of a main part. An enlarged cross-sectional view (b) of a main part is shown together with an explanatory view (a) showing completion of raising of the trigger lever. The main part enlarged sectional view (b) is shown together in the explanatory view (a) showing the state immediately before the engagement of the engaging claw and the clutch engaging part. Explanatory drawing which shows the state which the tooth | gear part has engaged with the gear tooth of the ratchet wheel. Explanatory drawing which shows the state in which the rotation locus | trajectory of a tooth | gear part crosses a gear tooth. Explanatory drawing which shows the state which a tooth | gear part leaves | separates from the gear tooth of a claw wheel. The main part enlarged sectional view (b) is shown together in explanatory drawing (a) which shows the state which changed to the clutch non-engagement state. The perspective view of a friction clutch mechanism. The principal part expanded sectional view of one Example which shows the moment when the engaging claw of the clutch member engaged with the clutch engaging part of the trigger lever. The principal part expanded sectional view of the other Example which shows the moment when the engaging claw of the clutch member engaged with the clutch engaging part of the trigger lever. The principal part expanded sectional view which shows another Example.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Feeding device, 2 hopper, 2a Swing fulcrum of hopper, 3 Feeding tray, 4 Feeding roller shaft, 5 Feeding roller, 6 Auxiliary roller, 7 Separation pad, 9 Medium return lever, 10 Tip of medium return lever , 11 Drive transmission system, 13 cam shaft, 15 hopper operation member, 16 cam transmission return member, 17 return action member, 19 drive motor, 21 gear, 21a gear, 41 cam shaft gear, 43 first cam, 45 second cam 47 Base frame, 48 Bearing portion, 49 Hopper pressing portion, 50 Rotating shaft of hopper operating member, 51 Second cam receiving portion, 52 Movement restriction degree hitting portion, 53 Torsion spring, 55 Hopper working end, 57 First cam Receiving portion, 59 spring locking portion, 61 guide plate, 63 guide gap, 65 coil spring, 67 shaft portion, 68 shaft end, 69 lever base, 70 slide plate, 71 twist , 73 cam guided portion, 75 notch, 77 cam guide surface, 78 feed shaft of feed roller, 79 gear teeth of claw wheel, 81 output pinion of drive motor, 83 first gear, 85 second gear, 87 Third gear, 89 Fourth gear, 91 Fifth gear, 92 Claw wheel, 93 Clutch member, 94 Tooth part, 95 Torsion coil spring, 96 Oscillating fulcrum, 97 Clutch auxiliary member, 98 Engaging claw, 99 Sixth gear , 100 engaging convex part, 101 seventh gear, 111 eighth gear, 113 lever shaft, 115 trigger lever, 116 arm, 117 compression spring, 119 driven differential gear, 121 friction clutch mechanism, 123 clutch engaging part, 125 Engagement surface of engagement claw, 127 engagement surface of clutch engagement part, 129 engaged convex part, 131 non-transmission part, 133 cylindrical base part, 135 annular part, 137 Storage part, 139 Sliding contact piece, 141 Rotating locus of clutch engaging part, 143 arrow, 145 First end of engaging convex part, 147 Second end of engaging convex part, 149 Top part of second cam, 151 cam Slope, 153 recess, 155 spaced apart, 156 tooth tip side of gear tooth side, 157 tooth trajectory, 160 high friction member, 161 high friction member, 170 carriage, 171 guide shaft

Claims (7)

A clutch device for turning on and off power transmission from a drive side gear driven to rotate by a drive motor to a driven system,
An engaging claw and a tooth portion engageable with the drive side gear and swingable about a swing fulcrum. By swinging, the clutch between the tooth portion and the drive side gear A clutch member that is switchable between an engaged state and a clutch non-engaged state, and is constantly biased by the clutch biasing means so as to swing to the clutch engaged state side;
An arm rotatable about a rotation fulcrum; and a clutch engaging portion provided on the arm and engageable with the engaging claw, wherein the clutch member and the driven system are engaged while rotating. A lever member that swings the clutch member to switch from the clutch engaged state to the clutch non-engaged state by engaging a claw with the clutch engaging portion;
A clutch device comprising engagement holding means for preventing disengagement due to an impact when the engaging claw and the clutch engaging portion are engaged.   2. The clutch device according to claim 1, wherein the engagement holding means is a high friction member provided on at least one of an engagement surface of the engagement claw and an engagement surface of the clutch engagement portion. The clutch device.   The clutch device according to claim 2, wherein the high friction member is a rubber material or a cork material.   The clutch device according to claim 1, wherein the engagement holding unit is configured by using a material of the lever member as a high friction material.   2. The clutch device according to claim 1, wherein the engagement holding means is a movable member provided at a position near the opposite side of the clutch member in a swing direction of the lever member so as to be on standby and movable. A clutch device characterized in that it is configured to restrict the swing of the lever by waiting.   A driving motor, a clutch device for turning on and off power transmission from a driving side gear driven to rotate by the driving motor to the driven system, and a feeding roller that applies a feeding force to the recording material are fixed, and A recording material feeding device comprising: a feeding roller shaft belonging to the driven system that is rotated by power transmitted from a driving gear, wherein the clutch device is any one of claims 1 to 5. A recording material feeding device comprising the clutch device according to claim 1.   A recording apparatus comprising: a recording material feeding device; and a recording execution unit that executes recording on the recording material fed from the recording material feeding device, wherein the recording material feeding device is A recording apparatus comprising the recording material feeding apparatus according to claim 6.

Images