Intermittent Drive Device

Abstract

To provide an intermittent driving device capable of saving space and stably switching operations.SOLUTION: An intermittent drive device 100 comprises an input gear 110, an output gear 120, a coupling member 130, and a toothless gear 170. The input gear 110 is provided with a first gear train 111 for receiving driving force, and a second gear train 112 for transmitting the driving force to the toothless gear 170. The coupling member 130 is a member that moves in a rotational axis direction to transmit the driving force of input gear 110 to the output gear 120 or cancel the transmission. Also, the intermittent drive device 100 comprises a toothless gear control mechanism that starts rotation of the toothless gear 170 in a state where the driving force from the input gear 110 is released and meshes with the input gear 110, and a switching mechanism that switches the position of the coupling member 130 in the rotational axis direction.SELECTED DRAWING: Figure 2

Description

[Technical field]

[0001] The present invention relates to an intermittent drive device. [Background technology]

[0002] Intermittent drive devices that repeatedly start and stop driving are used in various fields. For example, in a printer that transports paper and prints on the paper, the transport of the paper is temporarily stopped and then transport is resumed to synchronize the transport of the paper and the printing. To achieve this intermittent drive, a motor that quickly switches between rotation and stopping tends to be expensive or large, so a configuration is adopted in which a solenoid and a gear with missing teeth are used to continuously rotate an input gear that receives drive from the motor side, while transmitting a driving force to an output gear that transmits the driving force to other members, or the transmission is interrupted.

[0003] Patent documents 1 and 2 disclose intermittent drive devices that employ a solenoid and a tooth-missing gear and require a tooth-missing drive gear that drives the tooth-missing gear separately from the input gear.

[0004] Moreover, Patent Document 3 discloses an intermittent drive device that employs a solenoid and a tooth-missing gear, in which the input gear also drives the tooth-missing gear. [Prior art documents] [Patent documents]

[0005] [Patent Document 1] JP 2011-185293 A [Patent Document 1] JP 2008-164151 A [Patent Document 1] JP 2005-227315 A Summary of the Invention [Problem to be solved by the invention]

[0006] When the chipped gear is driven by a chipped drive gear separate from the input gear, the chipped gear can be driven at an appropriate speed independent of the rotational speed of the input gear, but this requires two drive systems, which can lead to an increase in size. Also, even in an intermittent drive device in which the input gear also drives the chipped gear, if the input gear has the same tooth row that receives drive from the drive source and the same tooth row that drives the chipped gear, the chipped gear cannot be driven at an appropriate speed and is unstable.

[0007] The present invention aims to provide an intermittent drive device that can save space compared to a configuration in which a missing-tooth gear is driven by a missing-tooth drive gear separate from the input gear, and that uses the input gear to drive the missing-tooth gear as well, and that can achieve stable operation switching compared to a configuration in which the tooth row by which the input gear receives drive from a drive source and the tooth row that drives the missing-tooth gear are the same tooth row. [Means for solving the problem]

[0008] First aspect The invention relates to A gear with a missing tooth, An output gear; an input gear having a first tooth row that receives a driving force and does not contact the chipped gear and a second tooth row that transmits a driving force to the chipped gear, the input gear being disposed at a position spaced apart from the output gear in the rotation axis direction; a coupling member that moves in a rotation axis direction to a first position where the driving force of the input gear is transmitted to the output gear and a second position where the transmission is released; a chipped gear control mechanism that starts rotation of the chipped gear from a state in which the driving force from the input gear is released, and meshes with the input gear; The intermittent drive device is characterized by comprising a switching mechanism for switching the position of the coupling member in the rotational axis direction between the first position and the second position.

[0009] Second aspect The invention relates to The tooth chipped gear control mechanism is a first spring member that biases the chipped gear in a direction toward meshing with the input gear when the driving force from the input gear is released; a solenoid having an arm that engages with the chipped gear when the driving force from the input gear is released to prevent rotation by the first spring member, and releases the engagement by energizing the solenoid. First aspect 2 is an intermittent drive device according to the first embodiment.

[0010] Third aspect The invention according to the present invention is characterized in that the tooth-missing gear has a claw portion on which the arm portion is hooked when the driving force from the input gear is released. Second aspect 2 is an intermittent drive device according to the first embodiment.

[0011] Fourth aspect The invention relates to The switching mechanism is a second spring member that biases the coupling member toward the first position; a moving member that is biased by the second spring member via the coupling member and that is movable together with the coupling member in the direction of the rotation axis and rotatable around the rotation axis; a cam member that rotates together with the toothless gear to interfere with the moving member and move the coupling member to a third position that is farther away from the first position than the second position; a first groove that interferes with the moving member to move the shaft coupling member to the first position, a second groove that holds the shaft coupling member at the second position, and a moving positioning member provided with a latch portion formed between the first groove and the second groove and having a slope for guiding the shaft coupling member into the first groove or the second groove, The movable member has an action portion which enters the first groove or the second groove of the latch portion or which contacts the inclined surface depending on a rotational position of the movable member. Any one of the first to third aspects 2 is an intermittent drive device according to the first embodiment.

[0012] Fifth aspect The invention relates to The moving member is an interference portion that interferes with the chipped gear when the shaft coupling member moves to the third position, The interference portion receives a rotational force from the tooth-missing gear, and the action portion rotates to a position corresponding to the inclined surface. Fourth aspect 2 is an intermittent drive device according to the first embodiment. Effect of the Invention

[0013] First aspect According to the intermittent drive device of the present invention, an intermittent drive device in which a tooth-missing gear is driven by an input gear and which is capable of stable operation switching is realized.

[0014] Second and third aspects According to the intermittent drive device of the present invention, the stop and rotation of the tooth-missing gear is controlled by the solenoid and the first spring member.

[0015] Fourth and fifth aspects According to the intermittent drive device of the present invention, the solenoid can be energized for a shorter period of time than in a configuration that does not use a movable positioning member. [Brief description of the drawings]

[0016] [Figure 1] FIG. 1 is a schematic diagram of an inkjet printer. [Diagram 2] FIG. 2 is a cross-sectional perspective view of the intermittent drive device. [Diagram 3] 3(A) and 3(B) are cross-sectional views showing an input gear and an output gear in a non-connected state (FIG. 3(A)) and a connected state (FIG. 3(B)). [Figure 4] 11 is an explanatory diagram of a latch mechanism including a slide member and a latch member. FIG. [Diagram 5] FIG. 13 is a diagram showing a clutch mechanism that switches between rotating and stopping the gear with missing teeth. [Figure 6] FIG. 6 is a diagram showing the same clutch mechanism as in FIG. 5, as viewed from the output gear side. [Figure 7] FIG. 4 is a diagram showing the clutch mechanism immediately after current is applied to the solenoid. [Figure 8] FIG. 13 is a diagram showing the clutch mechanism at an initial stage when rotation has started. [Figure 9] 11 is a cross-sectional view showing a state in which a slide member and a coupling member are pressed down by a cam member. FIG. [Figure 10] 11A and 11B are explanatory views of the operation of a latch mechanism formed by a slide member and a latch member. [Figure 11] 13A and 13B are diagrams illustrating the interaction between a toothless gear and a slide member. [Figure 12] 13 is a diagram showing the chipped gear and the slide member in a state in which the slide member is rotated by being pressed by the claw portion of the chipped gear. FIG. [Figure 13] 13 is a diagram showing the latch member and the slide member in a pushed-up state. FIG. [Figure 14] 13 is a diagram showing the latch member and the slide member in a state in which it has started to rotate after the post-shaped portion hits the inclined surface; FIG. [Figure 15] 13 is a diagram showing the latch member and the slide member in a state in which the pillar portion is inserted into the first groove. FIG. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0017] Hereinafter, an embodiment of the present invention will be described.

[0018] 1 is a schematic diagram of an inkjet printer, which employs an intermittent drive device according to one embodiment of the present invention.

[0019] The inkjet printer 10 is provided with an endless transfer belt 20. The transfer belt 20 is wound around a plurality of rolls 31, 32, and 33 and moves in a circular motion in the direction of arrow A.

[0020] The inkjet printer 10 is also provided with four print heads 40Y, 40M, 40C, and 40K above the transfer belt 20. These print heads 40Y, 40M, 40C, and 40K are inkjet type print heads that eject yellow, magenta, cyan, and black inks onto the transfer belt 20 in order to form ink images of each color on the transfer belt 20. When forming ink images of each color on the transfer belt 20, printing is performed in synchronization with the movement of the transfer belt 20 in the direction of arrow A so that a color ink image is formed on the transfer belt 20 as a whole.

[0021] As the transfer belt 20 moves, the ink image formed on the transfer belt 20 reaches a transfer position between a transfer roll 31, which is one of the multiple rolls 31, 32, and 33 around which the transfer belt 20 is wound, and a backup roll 50. Then, at this transfer position, the ink image formed on the transfer belt 20 is transferred onto a sheet of paper that has been transported to the transfer position. The transportation of the sheet of paper will be described later. After the ink image is transferred, the transfer belt 20 moves further, and its surface is cleaned by a cleaner 51, and the print heads 40Y, 40M, 40C, and 40K form an ink image on the transfer belt 20 again.

[0022] This inkjet printer 10 is equipped with two paper trays 60. Each paper tray 60 contains paper P in a stacked state. When printing, a pickup roll 71 picks up a sheet of paper P from one of the two paper trays 60, and a handling roll 72 reliably delivers only one sheet of paper. The delivered sheet of paper P is transported in the direction of arrow B by a transport roll 73 until the leading edge of the sheet of paper reaches a timing adjustment roll 74. The sheet of paper P delivered to the timing adjustment roll 74 is then delivered by the timing adjustment roll 74 so as to reach the transfer position at the timing when the ink image formed on the transfer belt 20 reaches the transfer position sandwiched between the transfer roll 31 and the backup roll 50.

[0023] The paper P to which the ink image has been transferred at the transfer position is then further transported on the transport belt 75. While being transported by the transport belt 75, the ink image on the paper P is dried by heat from the dryer 81, and a fixed image is formed on the paper P. The paper P is then sent out of the inkjet printer 10 by the delivery roll 76 in the direction of the arrow C.

[0024] Here, the paper P is transported so as to reach the timing adjustment roll 74 at a slightly earlier timing, and is sent by the timing adjustment roll 74 toward the transfer position at a timing synchronized with the ink image on the transfer roll 20. For this reason, the timing adjustment roll 74 repeats rotation and stopping. For this reason, an intermittent drive device 100 is provided here. Although the details will be described later, the intermittent drive device 100 includes an input gear that receives an input of a driving force and an output gear that transmits the driving force to the timing adjustment roll 74. A driving force from a motor (not shown) is continuously input to the input gear. Then, the intermittent drive device 100 transmits the driving force continuously input to the input gear to the output gear or blocks the transmission to the output gear according to control. The timing adjustment roll 74 stops or rotates upon receiving the intermittent driving force from the output gear.

[0025] The structure and operation of this intermittent drive device 100 will be described below.

[0026] 2 is a cross-sectional perspective view of the intermittent drive device 100. Here, the intermittent drive device 100 will be generally described with reference to this FIG.

[0027] This intermittent drive device 100 has a shaft member 102 supported by a base member 101. An input gear 110 is rotatably supported on the shaft member 102 directly above the base member 101, and an output gear 120 is rotatably supported at the top, away from the input gear 110 in the direction of the rotation axis.

[0028] The input gear 110 has a first gear train 111 formed around the bottom, and a second gear train 112 with a smaller diameter than the first gear train 111 formed around the top. Here, the second gear train 112 is shown with its unevenness for the purpose of explaining the interaction with the toothless gear 170 described later. On the other hand, the first gear train 111 is a gear train that simply receives the driving force transmitted from a motor (not shown), and does not come into contact with the toothless gear 170, and is shown here as a simple circle with the unevenness of the teeth omitted. Here, the input gear 110, the first gear train 111, and the second gear train 112 correspond to examples of the input gear, the first tooth train, and the second tooth train, respectively, in the present invention.

[0029] The output gear 120 has a gear train 121 formed around the maximum diameter portion. This gear train 121, like the first gear train 111 of the input gear 110, is shown as a simple circle with the projections and recesses of the teeth omitted. This gear train 121 plays a role in outputting a driving force toward the timing adjustment roll 74 shown in Fig. 1. This output gear 120 corresponds to an example of the output gear referred to in the present invention.

[0030] In addition to the input gear 110 and the output gear 120, a coupling member 130, a slide member 140, and a latch member 150 are provided around the shaft member 102, in that order from the input gear 110 side. A coil spring 160 is also provided around the shaft member 101.

[0031] The coupling member 130 plays a role in transmitting the driving force received by the input gear 110 to the output gear 120. The coupling member 130 is movable up and down along the shaft member 101, and is pushed up toward the output gear 120 by a coil spring 160 and engages with the output gear 120. When a cam member 180 (described later) presses down on the slide member 140, the coupling member 130 is also pressed down via the slide member 140, and the coupling member 130 separates from the output gear 120, and the transmission of the driving force to the output gear 120 is interrupted.

[0032] The slide member 140 rests on a shoulder portion 131 of the coupling member 130, and is pushed up together with the coupling member 130 by a coil spring 160. The slide member 140 is also pushed down by a cam member 180. Furthermore, the slide member 140 is latched in a pushed-down state by interference with the latch member 150, and is released from the latch and pushed by the coil spring 160, so that the slide member 140 is raised to a position where the coupling member 130 meshes with the output gear 120. The slide member 140 not only slides up and down together with the coupling member 130, but is also rotatable about the shaft member 101 in order to be latched to and released from the latch member 150.

[0033] Here, the coupling member 130, slide member 140, latch member 150, and coil spring 160 in the intermittent drive device 100 of this embodiment correspond to examples of the shaft coupling member, moving member, moving positioning member, and second spring member, respectively, as referred to in the present invention.

[0034] The intermittent drive device 100 further includes a toothless gear 170 , a cam member 180 , and a coil spring 190 .

[0035] 6, the toothless gear 170 is a gear in which a gear train 171 is not formed over the entire circumference, and a toothless region 172 where the gear train is missing is present. The toothless gear 170 is rotatably supported by a shaft portion 151 formed on a part of the latch member 150, and rotates while meshing with the second gear train 112 of the input gear 110, or stops rotating when the toothless region 172 faces the second gear train 112 and disengages from it.

[0036] The cam member 180 rotates or stops integrally with the toothless gear 170, and presses down the slide member 140 or releases the pressed-down state.

[0037] In addition, the coil spring 190 is hung between the base member 101 and the tooth-missing gear 170, and plays a role of pulling the tooth-missing gear 170 in a direction to rotate (the direction indicated by arrow Y) when, as shown in FIG. 6, the tooth-missing region 172 of the tooth-missing gear 170 faces the second gear train 112 and the meshing between the tooth-missing gear 170 and the second gear train 112 is released.

[0038] Although not shown in Fig. 1, as shown in Fig. 6, for example, the intermittent drive device 100 is provided with a solenoid 200. The solenoid 200 has an arm 201, and at the tip of the arm 201, a hook portion 201a is provided that hooks onto the claw portion 173 of the tooth-missing gear 170 to prevent the tooth-missing gear 170 from rotating.

[0039] Here, the toothless gear 170, the cam member 180, the coil spring 190, and the solenoid 200 in the intermittent drive device 100 correspond to an example of the toothless gear, the cam member, the first spring member, and the solenoid, respectively, according to the present invention. Also, the arm 201 with the hook portion 201a provided on the solenoid 200 corresponds to an example of the arm portion according to the present invention.

[0040] The interactions between the members constituting the intermittent driving device 100 shown in FIG. 1 will now be described.

[0041] Fig. 3 is a cross-sectional view showing the input gear and the output gear in a non-connected state (Fig. 3(A)) and a connected state (Fig. 3(B)). Note that in Fig. 3 and subsequent figures, basically only the members necessary for the explanation are shown, and members not necessary for the explanation are omitted.

[0042] In the non-coupled state shown in Fig. 3(A), the coupling member 130 and the slide member 140 are in a lowered position. The output gear 120 is provided with a gear train 121 for transmitting driving force to the outside, as well as a gear train 122 that meshes with the coupling member 130. In the non-coupled state shown in Fig. 3(A), the coupling member 130 is in a lowered position and is separated from the gear train 122 of the output gear 120.

[0043] In the connected state shown in Fig. 3(B), the coupling member 130 and the slide member 140 are in an elevated position. The input gear 110 is provided with a first gear train 111 that receives a driving force from an external source and a second gear train that meshes with the missing-tooth gear 170, as well as a gear train 113 that meshes with the coupling member 130. This gear train 113 is always meshed with the gear train 113 of the input gear 110, whether in the unconnected state shown in Fig. 3(A) or the connected state shown in Fig. 3(B). Therefore, the coupling member 130 rotates in conjunction with the rotation of the input gear 110, whether in the unconnected state or the connected state.

[0044] FIG. 4 is an explanatory diagram of a latch mechanism formed by a slide member and a latch member.

[0045] The latch member 150 has a latch portion 152 facing the slide member 140. In this latch portion 152, a first groove 153 cut deeply upward and a second groove 154 shallower than the first groove 153 are alternately formed at intervals in the circumferential direction. The first groove 153 and the second groove 154 are connected by an upward slope 155 extending from the first groove 153 to the second groove 154 and an upward slope 156 extending from the second groove 154 to the first groove 153.

[0046] Further, a columnar portion 141 that protrudes inward and extends in the vertical direction is formed on the slide member 140. This columnar portion 141 enters the first groove 153 or the second groove 154, or the upper end surface 141a of the columnar portion 141 contacts the upward slope 155 or the upward slope 156, depending on the rotational position of the slide member 140.

[0047] When the columnar portion 141 enters the first groove 153, the slide member 140 and the coupling member 130 move upward by being pushed by the coil spring 160, and as shown in Fig. 3(B), the coupling member 130 meshes with the gear train 122 of the output gear 120, resulting in a connected state in which driving force is transmitted from the input gear 110 to the output gear 120. This height position of the coupling member 130 moved upward by the columnar portion 141 entering the first groove 153 is referred to as the "first position" here.

[0048] Furthermore, when the columnar portion 141 enters the second groove 154, the slide member 140 and the coupling member 130 are latched in a state in which they are pressed downward, and as shown in Fig. 3(A), the coupling member 130 moves away from the output gear 120, resulting in a non-connected state in which no driving force is transmitted from the input gear 110 to the output gear 120. This height position of the coupling member 130 when it is in a state in which it is pressed downward by the columnar portion 141 entering the second groove 154 is referred to as the "second position" here.

[0049] As described above, the slide member 140 is pushed down by the cam member 180. The slide member 140 is in a state where the columnar portion 141 comes out of the first groove 153 or the second groove 154, and the upper end surface 141a of the columnar portion 141 is separated from the latch portion 152. The height position of the coupling member 130 in this state is referred to as the "third position" here.

[0050] Here, the latch portion 152 of the latch member 150 and the first groove 153 and second groove 154 of the latch portion 152 correspond to an example of the latch portion, the first groove, and the second groove, respectively, according to the present invention. Moreover, the upward slopes 155 and 156 of the latch portion 152 both correspond to an example of the slope, respectively, according to the present invention. Furthermore, the columnar portion 141 of the slide member 140 corresponds to an example of the action portion, respectively, according to the present invention.

[0051] Fig. 5 is a diagram showing a clutch mechanism for switching between rotation and stop of the tooth-missing gear. Fig. 5 is a diagram showing the shape as viewed from the base member 101 side.

[0052] FIG. 6 is a diagram showing the same clutch mechanism as FIG. 5, as viewed from the output gear side.

[0053] 5 and 6, the missing tooth region 172 of the missing tooth gear 170 is in a rotational position facing the second tooth row 112 of the input gear 110, and the missing tooth gear 170 is separated from the input gear 110. In this state, the missing tooth gear 170 is pulled in the direction of arrow X by the coil spring 190, and receives a rotational force in the direction of arrow Y. However, because the hook portion 201a at the tip of the arm 201 of the solenoid 200 is caught on the claw portion 173 of the missing tooth gear 170, the missing tooth gear 170 is prevented from rotating and maintains the rotational position shown in FIGS.

[0054] FIG. 7 is a diagram showing the clutch mechanism immediately after current is applied to the solenoid.

[0055] When the solenoid 200 is energized, the arm 201 is attracted by the magnetic force of the solenoid, and the hook portion 201a is disengaged from the claw portion 173. Then, the toothless gear 170 is pulled in the direction of the arrow X by the coil spring 190 and starts to rotate in the direction of the arrow Y.

[0056] FIG. 8 is a diagram showing the clutch mechanism in the initial stage after starting rotation.

[0057] When the toothless gear 170 starts to rotate in the direction of the arrow Y due to the action of the coil spring 190, a part of the gear row 171 of the toothless gear 70 meshes with the second tooth row 112 of the input gear 110, as shown in Fig. 8. Once meshed, the toothless gear 170 thereafter rotates due to meshing with the second tooth row 112 of the input gear 110.

[0058] Here, the input gear 110 is provided with a second gear train 112 that meshes with the toothless gear 170, separately from the first gear 111 that receives a driving force from a motor (not shown). Therefore, even in an intermittent drive device that rotates the input gear 110 at high speed, the toothless gear 170 can be rotated at a moderate speed by appropriately selecting the diameter of the second tooth train and the number of gears, thereby ensuring stable operation. If the input gear 110 does not have the second gear train 112 and the toothless gear 170 is driven by the first gear 111 that receives a driving force from the motor, the rotation speed of the input gear 110 is limited from the viewpoint of stable operation of the clutch mechanism, compared to the clutch mechanism of this embodiment in which the second gear train 112 is provided separately from the first gear train 111, in order to ensure stable operation of the clutch mechanism.

[0059] Alternatively, instead of driving the chipped gear 170 with the input gear 110, a configuration in which the chipped gear 170 is driven by a gear separate from the input gear 110 is also possible. However, in that case, two drive mechanisms are required, one for driving the input gear 110 and the other for driving the chipped gear 170, which may lead to an increase in size.

[0060] Returning to FIG. 8, the clutch mechanism of this embodiment will be further described.

[0061] When the state shown in FIG. 8 is reached, that is, when a part of the gear train 171 of the toothless gear 170 is engaged with the second gear train 112 of the input gear 110, it is no longer necessary to energize the solenoid 200, and the energization is cut off. When the energization is cut off, the arm 201 of the solenoid 200 returns to its original position, but the claw portion 173 of the toothless gear 170 has already passed, and the rotation of the toothless gear 170 continues as is. Then, when the toothless gear 170 makes one revolution and the toothless region 172 faces the second gear train 112 side, the hook portion 201a at the tip of the arm 200 is caught by the claw portion 173, and the gear stops at that rotation position, that is, the rotation position shown in FIG. 5 and FIG. 6. Here, the clutch mechanism described with reference to FIG. 5 to FIG. 8 corresponds to an example of the toothless gear control mechanism of the present invention.

[0062] When this tooth-missing gear 170 starts to rotate, if it was in the non-connected state shown in FIG. 3(A), it switches to the connected state shown in FIG. 3(B), or if it was in the connected state shown in FIG. 3(B), it switches to the non-connected state shown in FIG. 3(A).

[0063] This switching mechanism will now be described.

[0064] FIG. 9 is a cross-sectional view showing a state in which the slide member 140 and the coupling member 130 are pressed down by the cam member.

[0065] When the tooth-missing gear 170 starts to rotate, the cam member 180 also rotates together with the tooth-missing gear 170, and the slide member 140 is directly pressed down by the cam portion 181 of the cam member 180, and the coupling member 130 is also pressed down by the slide member 140.

[0066] FIG. 10 is an explanatory diagram of the operation of the latch mechanism formed by the slide member and the latch member.

[0067] The slide member 140 is pushed down to a height position shown in FIG. 10 by the latch portion 181 of the latch member 180. FIG. 10 shows that the columnar portion 141 of the slide member 140 was in the second groove 154 immediately before being pushed down. As described above, the height position of the coupling member 130 when the columnar portion 141 is in the second groove 154 is in the "second position" shown in FIG. 3(A) in which the coupling member 130 and the output gear 120 are disconnected from each other. FIG. 10 shows the slide member 140 in a state where the columnar portion 141 is pushed down until it is disengaged from the second groove 154. The coupling member 130 at this time is in a "third position" which is further pushed down than the "second position".

[0068] 10 shows the claw portion 142 of the slide member 140. When the slide member 140 is pressed down by the cam member 180, this claw portion 142 is at the same height as the claw portion 173 (see FIG. 6, for example) of the toothless gear 170. When the toothless gear 170 rotates, this claw portion 142 is in a position where it interferes with the claw portion 173 of the toothless gear 170.

[0069] FIG. 11 is a diagram showing the interaction between the toothless gear and the slide member.

[0070] A plurality of claws 142 are formed at equal intervals in the circumferential direction on the slide member 140. The intervals between the plurality of claws 142, i.e., the angle in the circumferential direction between adjacent claws, match the angle in the circumferential direction between a first groove 153 and a second groove 154 formed in the latch portion 152 of the latch member 150.

[0071] 11 shows a state in which the toothless gear 170 rotates in the direction of arrow Y and the claw portion 173 of the toothless gear 170 comes into contact with the claw portion 142 of the slide member 140. When the claw portion 173 of the toothless gear 170 comes into contact with the claw portion 142 of the slide member 140, the claw portion 173 of the toothless gear 170 is pressed by the claw portion 142 of the slide member 140 due to the subsequent rotation of the toothless gear 170, and the slide member 140 rotates in the direction of arrow Z until the claw portion 173 of the toothless gear 170 is disengaged from the claw portion 142 of the slide member 140. The claw portion 142 of the slide member 140 corresponds to an example of an interference portion according to the present invention.

[0072] FIG. 12 is a diagram showing the chipped gear and the slide member in a state in which the slide member is rotated by being pressed by the claw portion of the chipped gear.

[0073] 12, the slide member 140 is released from the downward pressure by the cam member 180. Then, the slide member 140 is pushed up together with the coupling member 130 by the coil spring 160.

[0074] FIG. 13 is a diagram showing the latch member and the slide member in a pushed-up state.

[0075] As described above, the slide member 140 rotates slightly due to the interference between the claw portion 173 and the claw portion 142, and in this rotated state, it is released from being pressed down by the cam member 180. Then, as shown in Fig. 13, the top 141a of the columnar portion 141 of the slide member 140 hits the upward slope 156 at a position slightly off from directly below the second groove 154. The position where the top 141a of the columnar portion 141 hits is the upward slope 156, and since the slide member 140 is further pressed by the coil spring 160, the slide member 140 continues to rotate further in the direction of the arrow Z.

[0076] FIG. 14 is a diagram showing the latch member and the slide member in a state where the post portion has hit the inclined surface and has started to rotate.

[0077] FIG. 15 is a view showing the latch member and the slide member in a state where the pillar portion is inserted into the first groove.

[0078] When the slide member 140 is released from the downward pressure of the cam member 180 and pushed up by the coil spring 160, the top 141a of the columnar portion 141 hits the upward slope 156 as shown in FIG. 13. Then, the coil spring 160 further pushes up, and the top 141a of the columnar portion 141 advances along the upward slope 156 as shown in FIG. 14. That is, the slide member 140 rotates in the direction of the arrow Z while being pushed up by the coil spring 160. Then, finally, as shown in FIG. 15, the rotation of the slide member 140 stops with the columnar portion 141 inserted into the first groove 153. At this time, the coupling member 130 is raised to the "first position", that is, the height position where the coupling state shown in FIG. 3(B) is achieved.

[0079] When switching the connected state shown in FIG. 3(B) to the unconnected state shown in FIG. 3(A), the same switching operation as that when switching the unconnected state shown in FIG. 3(A) to the connected state shown in FIG. 3(B) is performed. That is, the solenoid 200 is energized and the toothless gear 170 rotates. Then, the slide member 140 is pushed down by the cam member 180 rotating together with the toothless gear 170, and the columnar portion 141 comes out of the first groove 153. Then, the claw portion 173 of the toothless gear 170 pushes the claw portion 142 of the slide member 140, and the slide member 140 rotates a little. Then, at that stage, the slide member 140 is released from being pushed down by the cam member 180. Then, the slide member 140 is pushed up by the coil spring 10, and the top portion 141a of the columnar portion 141 hits the upward slope 155. Then, due to further upward pressure by the coil spring 160, the slide member 140 rotates, and the columnar portion 141 enters the second groove 154. When the columnar portion 141 enters the second groove 154, the rotation of the slide member 140 stops. When the columnar portion 141 of the slide member 140 enters the second groove 154, the coupling member 130 is lifted up to the "second position". This "second position" is the height position of the non-coupled state shown in FIG. 3(A), and this non-coupled state is maintained until the solenoid 200 is next energized.

[0080] As described above, according to the intermittent drive device 100 of this embodiment, the first gear train 111 and the second gear train 112 are formed on the input gear 110, so that the intermittent drive device can be designed to rotate the chipped gear 170 at an appropriate rotation speed for stable operation, even in an intermittent drive device designed to rotate the input gear 110 at high speed. Also, the intermittent drive device 100 requires only one drive system, which allows for a smaller size compared to a configuration in which a drive system for driving the input gear and a drive system for driving the chipped gear are separate systems.

[0081] Furthermore, since the intermittent drive device of this embodiment is provided with the above-mentioned latch mechanism, it is possible to switch between a non-connected state and a connected state by passing current through the solenoid for a short period of time, thereby achieving power saving.

[0082] Although the intermittent drive device has been described here as being applied to an inkjet printer, the intermittent drive device of the present invention is not limited to inkjet printers, but can also be applied to printers of various types, such as electrophotographic printers. Furthermore, the application field of the intermittent drive device of the present invention is not limited to printers, but can be widely applied to cases where a driven object to be driven needs to be driven intermittently. [Explanation of symbols]

[0083] 10. Inkjet Printer 100 Intermittent drive device 101 Base material 102 Shaft member 110 Input Gear 111 First Gear Train 112 2nd Gear Train 120 Output Gear 130 Coupling parts 131 Shoulder of coupling member 140 Slide member 141 Columnar part 141a Upper end surface of column 142 Claw portion of slide member 150 Latch member 152 Latch section 153 First groove 154 2nd groove 155, 156 Uphill 160 Coil spring 170 Gear with missing teeth 172 Tooth chipping area 173 Claw 180 Cam member 181 Cam section 190 Coil spring 200 Solenoid 201 Arm 201a Hook part

Claims

1. A gear with a missing tooth, An output gear; an input gear having a first tooth row that receives a driving force and does not contact the chipped gear and a second tooth row that transmits a driving force to the chipped gear, the input gear being disposed at a position spaced apart from the output gear in the rotation axis direction; a coupling member that moves in a direction of a rotation axis between a first position where the driving force of the input gear is transmitted to the output gear and a second position where the transmission is released; a chipped gear control mechanism that starts rotation of the chipped gear from a state in which the driving force from the input gear is released, and meshes with the input gear; a switching mechanism for switching a position of the coupling member in a rotational axis direction between the first position and the second position.

2. The tooth chipped gear control mechanism is a first spring member that biases the chipped gear in a direction toward meshing with the input gear when the driving force from the input gear is released; a solenoid having an arm that is hooked onto the chipped gear when the driving force from the input gear is released to prevent the gear from being rotated by the first spring member and that is released from the hooking by energization; 2. The intermittent drive device according to claim 1, further comprising:

3. 3. The intermittent drive device according to claim 2, wherein the tooth-missing gear has a claw portion with which the arm portion is hooked when the driving force from the input gear is released.

4. The switching mechanism is a second spring member that biases the coupling member toward the first position; a moving member that is biased by the second spring member via the coupling member and that is movable together with the coupling member in the direction of the rotation axis and rotatable about the rotation axis; a cam member that rotates together with the toothless gear to interfere with the moving member and move the coupling member to a third position that is farther away from the first position than the second position; a moving and positioning member provided with a latch portion having a first groove that interferes with the moving member to move the shaft coupling member to the first position, a second groove that holds the shaft coupling member at the second position, and a slope formed between the first groove and the second groove for guiding the shaft coupling member into the first groove or the second groove, 4. An intermittent drive device according to claim 1, wherein the movable member has an action portion that enters the first groove or the second groove of the latch portion, or that contacts the inclined surface, depending on the rotational position of the movable member.

5. The moving member is an interference portion that interferes with the chipped gear when the shaft coupling member moves to the third position, 5. The intermittent drive device according to claim 4, wherein the interference portion receives a rotational force from the tooth-missing gear, and the action portion rotates to a position corresponding to the inclined surface.

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