JP4453811B2 - Gap adjusting device, recording device, liquid ejecting device - Google Patents

Description

  The present invention relates to a gap adjusting device that adjusts a gap between a recording head and a recording medium, and a recording device that includes the gap adjusting device. The present invention also relates to a liquid ejecting apparatus.

  Here, the liquid ejecting apparatus uses an ink jet recording head, and is not limited to a recording apparatus such as a printer, a copying machine, and a facsimile machine that discharges ink from the recording head to perform recording on a recording medium. And a device that ejects the liquid corresponding to the application from the liquid ejecting head corresponding to the ink jet recording head to the ejected medium corresponding to the recording material, and adheres the liquid to the ejected medium. .

  In addition to the recording head, as a liquid ejecting head, a color material ejecting head used for manufacturing a color filter such as a liquid crystal display, and an electrode material (conductive paste) used for forming an electrode such as an organic EL display or a surface emitting display (FED) Examples thereof include an ejection head, a bioorganic matter ejection head used for biochip production, and a sample ejection head as a precision pipette.

  One of the recording apparatuses is an ink jet printer. In the ink jet printer, an ink jet recording head is provided at the bottom of a carriage that reciprocates in the main scanning direction. The carriage is reciprocated in the main scanning direction by receiving the driving force of the motor while being guided by a carriage guide shaft extending in the main scanning direction.

  Here, the ink jet printer is provided with a gap adjusting device for adjusting the gap between the ink jet recording head and the recording medium in order to appropriately perform recording for each recording medium having a different thickness. In this gap adjusting device, a bush member having a rotation center is provided at a position shifted from the axis of the carriage guide shaft exclusively at the shaft end of the carriage guide shaft, and by rotating the bush member, It is comprised so that a height position may be changed up and down (refer patent document 1). Further, a plurality of carriage guide shafts (for example, two) are provided, and the bushing members attached to the shaft ends of the plurality of carriage guide shafts are rotated synchronously, thereby increasing the height of the plurality of carriage guide shafts. Some are configured to move up and down at the same time (see Patent Document 2).

  Most of the conventional gap adjusting devices as described above have two gap adjusting positions, and the two gap adjusting positions are switched by an adjusting lever or the like that engages with the bush member and rotates the bush member. (Refer patent document 3). Or in patent document 2, it is comprised so that two gap positions may be switched using the driving force of a motor. The two gap adjustment positions are configured to be held by the biasing force of the coil spring.

  That is, a coil spring that engages with the adjusting lever is provided so that the urging direction is switched at an approximately middle position between the first gap position and the second gap position, and each gap is held at each gap position. As is done, an urging force is applied to the adjusting lever. Assuming that the first gap position is on the small gap side and the second gap position is on the large gap side, the bush member is moved to the first gap position by the weight of the carriage guide shaft and the carriage at the second gap position. It is easy to rotate to the gap position side. Therefore, in order to reliably hold the second gap position in particular, it is necessary to further increase the biasing force of the coil spring.

JP-A-8-300769 Japanese Patent Application Laid-Open No. 10-211748 Japanese Patent Laid-Open No. 2002-36660

By the way, when the gap adjustment is performed using the driving force of the motor, it is necessary to rotate the bush member against the urging force of the coil spring. For example, the conveying roller for conveying the recording medium is driven to rotate. In order to obtain power from the motor for this purpose, it is necessary to select the motor in consideration of the biasing force of the coil spring, which causes a cost increase. In particular, the gap adjusting device disclosed in Patent Document 2 includes two carriage guide shafts, which further increases the load on the motor.
On the other hand, in the conventional gap adjusting device described above, since the two gap positions of the first gap position and the second gap position are held by the coil spring, there are three gap positions. It was not possible to set more.

  Therefore, the present invention has been made in view of such a situation, and the problem is that a gap adjusting device that can perform gap adjustment with a small rotational torque and that can set more gap positions. There is to get.

  In order to solve the above-described problems, a first aspect of the present invention provides a recording apparatus including a carriage including a recording head that performs recording on a recording medium, and a carriage guide shaft that guides the carriage in the main scanning direction. A gap adjusting device for adjusting a gap between the recording head and the recording medium by adjusting a height position of the carriage guide shaft, wherein the member is attached to a shaft end of the carriage guide shaft, and The carriage guide shaft is rotatably provided on a side frame that is erected so as to be orthogonal to the axial direction of the carriage guide shaft, and the carriage guide shaft is arranged so that the center of rotation does not coincide with the axis of the carriage guide shaft. A bushing member that supports the shaft, and a bushing portion that engages with the bushing member and rotates the bushing member and receives the power of the motor. Rotating means, and a sliding member provided so that the bush member rotating means slides along the surface of the side frame under the power of the motor, and the sliding movement of the sliding member. A slide member locking means for restraining, a bush member engaging portion that engages with the bush member, and a boss portion loosely inserted into a cam groove formed in the slide member, and provided rotatably. A bush member rotating member that rotates when the boss portion is displaced in the cam groove in accordance with a sliding operation, thereby rotating the bush member, and the bush member and the bush member rotating member are Due to the weight of the carriage and the carriage guide shaft acting on the boss portion via the boss portion, the boss portion The cam surface of the rectangular side, wherein the is configured so as to displace the cam groove while pressed in a direction intersecting the sliding direction of the sliding member.

  According to the first aspect, the gap adjusting device includes the bush member attached to the shaft end of the carriage guide shaft, the bush member rotating member that rotates the bush member, and the bush member rotating member. A slide member to be moved. Then, by the sliding operation of the slide member, the boss portion provided on the bush member rotating member displaces in the cam groove formed on the slide member, whereby the bush member rotating member rotates to rotate the carriage guide shaft. The height position changes. Here, the weights of the carriage and the carriage guide shaft act on the boss portion via the bush member and the bush member rotating member, whereby the boss portion slides on the cam surface on one side of the cam groove. The cam groove is displaced while being pressed in a direction crossing the sliding direction of the member. Accordingly, since the weight of the carriage guide shaft and the carriage guide shaft is not directly applied to the slide direction of the slide member but to the direction intersecting the slide direction of the slide member, the height position of the carriage is changed with a small force. In addition, the gap position can be maintained. In other words, the gap can be adjusted with a small rotational torque, and more gap positions can be set.

  According to a second aspect of the present invention, in the first aspect, the slide member includes the boss portion loosely inserted into the cam groove in the entire range in which the bush member rotating member can rotate. It has a bending restricting means for restricting the bending of the bushing member rotating member in the direction of dropping from the cam groove and preventing the boss portion from dropping from the cam groove. It is a gap adjusting device.

  When the boss portion of the bush member rotating member is displaced in the cam groove by the sliding movement of the slide member and the bush member rotating member rotates, the inner wall of the cam groove with which the boss portion is in contact with the boss portion. By pushing, the boss portion is displaced along the shape of the cam groove while being in sliding contact with the inner wall of the cam groove. At that time, the inner wall of the cam groove with which the boss portion is in sliding contact pushes the boss portion, so that the force that deflects the bush member rotating member in the direction in which the boss portion loosely inserted into the cam groove falls off is applied to the bush. It acts on the member rotating member. Therefore, if the bush member rotating member is greatly bent by the force, the boss portion may fall off the cam groove. Therefore, a bending restricting means for restricting the bending of the bushing member rotating member in the direction in which the boss part loosely inserted into the cam groove falls off from the cam groove in the entire range in which the bushing member rotating member can be rotated. Provide. As a result, when the boss portion of the bushing member rotating member is displaced in the cam groove by the sliding operation of the sliding member and the bushing member rotating member rotates, the bushing member rotating member is greatly bent and is allowed to play in the cam groove. It is possible to prevent the inserted boss portion from falling off the cam groove.

  According to a third aspect of the present invention, in the second aspect, the bending restricting means abuts in the vicinity of the boss portion of the bush member rotating member, and the boss portion can be displaced in the cam groove. A guide wall is formed along the cam groove to regulate the bending of the bush member rotating member in a direction in which the boss part loosely inserted in the cam groove in a state is dropped from the cam groove. Is a gap adjusting device.

  As described above, the guide wall is formed along the cam groove so as to slide in contact with the bush member rotating member in the vicinity of the boss portion and lock the boss portion from falling off the cam groove while the boss portion can be displaced in the cam groove. By doing so, the vicinity of the boss part displaced in the cam groove always abuts against the guide wall. As a result, the bending of the bushing member rotating member in the direction in which the boss part is removed from the cam groove is restricted, so that the boss part of the bushing member rotating member is displaced in the cam groove by the sliding operation of the sliding member. When the rotating member rotates, it is possible to prevent the bush member rotating member from being greatly bent and the boss portion loosely inserted into the cam groove from falling off the cam groove.

According to a fourth aspect of the present invention, in any one of the first to third aspects, the cam groove changes the gap so that the gap is gradually adjusted to a plurality of gap positions. A change portion and a non-change portion that does not change the gap are provided and formed in a staircase shape.
According to the fourth aspect, the gap does not change in a state where the boss portion is in the non-change portion, and therefore the gap can be stably held in the state.

According to a fifth aspect of the present invention, in the fourth aspect described above, the gap is switched in three stages by providing three non-change parts.
According to the fifth aspect, since the gap is configured to be switched in three stages by providing the three non-change portions, the gap is automatically switched with a minimum motor torque. Is possible.

  According to a sixth aspect of the present invention, in any one of the first to fifth aspects, the bushing member rotating means meshes with a rack formed on the slide member and the power of the motor And a gear wheel train provided on the side frame, and configured to slide the slide member by the rotation of the pinion gear. One of the gears is configured to be slidable in the direction of the rotation axis, so that the power transmission of the motor can be cut off from the tooth wheel train, and the sliding operation of the one gear However, the carriage includes a biasing means for biasing the one gear in a direction in which the one gear meshes with another gear, and an arc-shaped hole formed in the side frame. The engagement pin provided on the one gear so as to protrude into the inspection region is configured to be performed by the carriage that presses the one gear in a direction away from the tooth wheel train. Features.

  According to the sixth aspect, the sliding movement of the sliding member is performed by transmitting the driving force of the motor through the toothed wheel train, and one gear constituting the toothed wheel train is pushed by the carriage. Therefore, the power transmission from the motor can be cut off, so that the motor can be transported to another motor (for example, transporting a recording medium). It can be easily combined with a conveyance motor for rotating the roller.

According to a seventh aspect of the present invention, in the sixth aspect, the motor is a conveyance motor that rotationally drives a conveyance roller that conveys a recording medium.
According to the seventh aspect, since the motor for adjusting the gap is also used as a conveyance motor that rotationally drives the conveyance roller that conveys the recording medium, the cost can be reduced and the first aspect can be achieved. Due to the operational effect of this aspect, the gap can be adjusted with a small rotational torque.

According to an eighth aspect of the present invention, in the sixth aspect or the seventh aspect, the slide member locking means is formed on the engagement protrusion formed on the disk surface of the one gear and the side frame. A plurality of insertion holes formed so as to be localized at positions where the engagement protrusions are located at a plurality of gap positions. And
According to the eighth aspect, in the slide member locking means, the engagement protrusion formed on the disk surface of one gear constituting the toothed wheel train is fitted into the insertion hole formed in the side frame. Accordingly, the slide member is locked by stopping the rotation of the one gear. And since the said insertion hole is formed in multiple numbers so that it may localize in the position where the said protrusion for engagement is located in several gap position, it can hold | maintain reliably by several gap position.

According to a ninth aspect of the present invention, in any one of the first to eighth aspects, the carriage is guided by the two carriage guide shafts provided at a predetermined interval in the sub-scanning direction. The bush member rotating member is disposed between the two carriage guide shafts and simultaneously rotates the bush members attached to the shaft ends of the two carriage guide shafts. It is characterized by being configured in various ways.
According to the ninth aspect, the recording apparatus includes the two carriage guide shafts, and the gap adjusting device includes the bush member rotating member between the two carriage guide shafts. Since the two carriage guide shafts are simultaneously rotated by the member, the height position of the two carriage guide shafts can be changed while simplifying the structure and easily synchronizing.

According to a tenth aspect of the present invention, there is provided a carriage including a recording head for recording on a recording medium, a carriage guide shaft for guiding the carriage in the main scanning direction, and adjusting a height position of the carriage guide shaft. A gap adjusting device for adjusting a gap between the recording head and a recording medium, wherein the gap adjusting device is described in any one of the first to ninth aspects. It is the gap adjusting device.
According to the tenth aspect, in the recording apparatus, it is possible to obtain the same operational effects as those of the first to ninth aspects described above.

  According to an eleventh aspect of the present invention, a carriage including a liquid ejecting head that ejects liquid onto an ejected medium, a carriage guide shaft that guides the carriage in the main scanning direction, and a height position of the carriage guide shaft are adjusted. A gap adjusting device that adjusts a gap between the liquid ejecting head and the ejection target medium, wherein the gap adjusting device is a member attached to the shaft end of the carriage guide shaft. In addition, the carriage guide is rotatably provided on a side frame that is erected so as to be orthogonal to the axial direction of the carriage guide shaft, and the rotation guide and the axis of the carriage guide shaft do not coincide with each other. A bush member that pivotally supports the shaft, and engages with the bush member to rotate the bush member. A bush member rotating means, and the bush member rotating means is provided so as to slide along the surface of the side frame under the power of the motor, and the slide of the slide member The slide member locking means for restricting the operation, a bush member engaging portion that engages with the bush member, and a boss portion that is loosely inserted into a cam groove formed in the slide member, and is provided rotatably. A bush member rotating member that rotates when the boss portion is displaced in the cam groove in accordance with a sliding operation of the member, thereby rotating the bush member, and the bush member and the bush member rotating Due to the weight of the carriage and the carriage guide shaft acting on the boss portion via a member, the boss portion is moved forward. The cam surface of one side of the cam groove, wherein the is configured so as to displace the cam groove while pressed in a direction intersecting the sliding direction of the sliding member.

Hereinafter, an embodiment of the present invention will be described with reference to the drawings.
First, a schematic configuration of an inkjet printer (hereinafter referred to as “printer”) 1 as an example of a “recording apparatus” and a “liquid ejecting apparatus” according to the present invention will be described with reference to FIGS. Here, FIG. 1 is an external perspective view of the printer 1, FIG. 2 is an external perspective view of the printer 1 with the external housing removed, and FIG. 3 is a schematic side sectional view of the printer 1.

  As shown in FIG. 1, it is assumed that the printer 1 has a box shape, is approximately the size of a video tape recorder, and is used in a state of being stored in a TV rack or the like. It is configured. As shown in the figure, a front cover 8 is provided on the front surface of the box-shaped housing 3 so as to be roughly configured, and the front cover 8 is opened toward the front side (used state: not shown). A closed state (non-use state) is rotatably provided. In the open state, the recording paper on which recording has been performed can be ejected, and the disk tray 33 (see FIG. 2) can be taken in and out. A paper feed tray 30 is detachably provided at the lower portion of the front cover 8, and the recording paper can be set by being pulled out and removed. An ink cartridge unit 15 is provided above the front cover 8, and a plurality of ink cartridges 16 (see FIG. 3) are detachably provided side by side in the width direction of the printer 1.

  Next, the internal configuration of the printer 1 will be outlined with reference to FIGS. In FIG. 2, the apparatus main body of the printer 1 includes a lower chassis 4, a main frame 5 extending in the width direction (main scanning direction) of the apparatus main body, and a depth direction of the apparatus main body standing on both sides of the main frame 5. The base is constituted by the side frame right 6 and the side frame left 7 which are parallel to the (sub-scanning direction). Between the side frame right 6 and the side frame left 7, a main carriage guide shaft 11 and a sub carriage guide shaft 12 extending in the main scanning direction are pivotally supported at a predetermined interval in the sub scanning direction.

  The main carriage guide shaft 11 and the sub carriage guide shaft 12 are guide shafts for guiding the carriage 13 in the main scanning direction, the main carriage guide shaft 11 is inserted through the rear portion of the carriage 13, and the sub carriage guide shaft 12 is the carriage 13. The distance between the recording head 14 (FIG. 3) and the recording paper P (paper gap: hereinafter referred to as “PG”) is defined. The gap adjusting device 50 according to the present invention is provided on the left side frame 7 (however, members (not shown) corresponding to bush members 67 and 68 described later are also provided on the right side frame 6 side). The PG is adjusted by adjusting the height positions of the main carriage guide shaft 11 and the sub-carriage guide shaft 12, which will be described in detail later.

  Next, the conveyance path of the recording paper P and the disc tray 33 will be described with reference to FIG. As described above, the printer 1 includes the paper feed tray 30 that is detachable at the bottom of the apparatus. A plurality of recording papers P can be set in a stacked state on the paper feed tray 30, and a hopper 31 is provided at the bottom thereof. The hopper 31 is provided so as to be swingable about a swing shaft 31a, and presses the set recording paper P from below to press the bundle of recording paper P against the feeding roller 28 provided at the top.

  The feeding roller 28 has a substantially D shape in a side view, and the outer periphery is formed by a high friction member (for example, a rubber material). When the recording paper P is fed, the uppermost recording paper P in pressure contact with the arc portion of the feeding roller 28 is fed to the downstream side (the right side in FIG. 3) by the rotation of the feeding roller 28. In addition, friction separating means (not shown) that presses against the arc portion of the feeding roller 28 is provided below the feeding roller 28, and a recording sheet is provided between the friction separating means and the feeding roller 28. By pinching P, the uppermost recording sheet P to be fed is separated from the next and subsequent recording sheets P to be fed.

  On the downstream side of the feeding roller 28, a conveyance driving roller 21 that is rotationally driven by a conveyance motor 40 (see FIG. 4) and a conveyance driven roller 22 that is driven to rotate in contact with the roller are provided. The recording paper P is conveyed under the recording head 14 by nipping the paper P and rotating the conveyance driving roller 21. The recording head 14 and the platen 20 are provided on the downstream side of the transport driving roller 21 so as to face each other in the vertical direction. The transported recording paper P is supported by the recording head 14 from the bottom in a state of being supported from below. Recording is performed by ejecting (ejecting) ink droplets as “liquid”. Although the recording head 14 is provided at the bottom of the carriage 13, no ink cartridge is mounted on the carriage 13 that reciprocates in the main scanning direction, and as described above, on the upper side of the main scanning area of the carriage 13. A plurality of ink cartridges 16 are detachably arranged side by side in the main scanning direction. Then, ink is supplied to the carriage 13 via an ink tube (not shown).

  On the downstream side of the recording head 14, there are provided a discharge driving roller 23 that is rotationally driven by the conveying motor 40, and a discharge driven roller 24 that is driven and rotated in contact with the roller. The recording paper P is discharged to the outside of the printer 1 by rotating the discharge driving roller 23.

  On the other hand, a disc tray 33 on which an optical disc D represented by a DVD (Digital Versatile Disk) or the like can be set is disposed above the paper feed tray 30. A rack (not shown) is formed at the side end of the disk tray 33, and is configured to move substantially horizontally and straight by rotation of a pinion gear (not shown) that meshes with the rack. At the time of recording on the optical disk D, after the tray tip is transported by the moving means until it is nipped between the transport driving roller 21 and the transport driven roller 22, the recording head receives the driving force due to the rotation of the transport driving roller 21. 14 is conveyed at a predetermined pitch and recording is performed.

  The above is the outline of the printer 1, and the configuration of the gap adjusting device 50 for adjusting PG will be described in detail below with reference to FIGS. 4 is an external perspective view of the gap adjusting device 50, FIG. 5 is an exploded perspective view of the gap adjusting device 50, and FIG. 6 is an external perspective view of the gap adjusting device 50 as viewed from the back side (the state without the side frame left 7). 7 is a perspective view of the same (with the side frame left 7), FIG. 8 is a view showing the relationship between the rotation center of the bush member and the axis of the carriage guide shaft, and FIGS. It is a front view and is a figure which shows operation | movement transition of the gap adjustment apparatus 50. 12 to 15 are diagrams showing a control flow at the time of PG switching.

  As shown in FIGS. 4 and 5, the gap adjusting device 50 includes bush members 67 and 68. The bush member 67 is attached to the shaft end of the main carriage guide shaft 11 on the side frame left 7 side, and the bush member 68 is similarly attached to the shaft end of the sub carriage guide shaft 12 on the side frame left 7 side. The bush members 67 and 68 are rotatably attached to the left side frame 7 via an intermediate member (not shown).

The sub-carriage guide shaft 12 will be described as an example. As shown in FIG. 8, a half-moon-shaped mounting portion (projection) 12a is formed at the shaft end of the sub-carriage guide shaft 12, and the mounting portion 12a is a bush member. It is press-fitted into a half-moon shaped insertion hole formed in 68. Here, reference numeral C ₁ indicates the rotation center of the bush member 68, and reference numeral C ₂ indicates the axis of the sub carriage guide shaft 12. As shown in the drawing, the rotation center C ₁ and the shaft center C ₂ are configured so as not to coincide with each other. Therefore, when the bush member 68 provided on the left side frame 7 is rotated, the height of the auxiliary carriage guide shaft 12 is increased. The PG can be adjusted. The same applies to the bush member 67 attached to the main carriage guide shaft 11 side. Therefore, the gap adjusting device 50 transmits the rotation of the conveying motor 40 to the bush members 67 and 68 via the tooth wheel train to be described later, and rotates the bush members 67 and 68 in synchronism to thereby rotate the main carriage guide. The PG is adjusted while maintaining the height position of the shaft 11 and the sub carriage guide shaft 12 to be the same.

In the present embodiment, as shown in FIG. 8, the axis of the bush member 68 in front view rotation center C ₁ by-carriage guide shaft 11 (bushing member 67) (main carriage guide shaft 12) C ₂ The sub-carriage guide shaft 11 (main carriage guide shaft 12) and the own weight of the carriage 13 act on the bush member 68 (bush member 67) as shown in the figure. A force that turns clockwise is applied.

  Next, each of the bush members 67 and 68 is formed so that the outer periphery can engage with the gear, and each of the bush members 67 and 68 is a gear portion as a “bush member engaging portion” in the intermediate gear 65 as a “bush member rotating member”. It meshes with 65a and 65b. The intermediate gear 65 is pivotally supported by a shaft 74 and has a boss 65c that protrudes to the left side 7 of the side frame in the vicinity of the gear portion 65a.

  The boss 65 c is loosely inserted into a cam groove 53 formed in the slide member 51 and having a step shape extending in the sliding direction of the slide member 51, thereby displacing the cam groove 53 in accordance with the slide operation of the slide member 51. As a result, the intermediate gear 65 rotates. The slide member 51 is attached so as to slide horizontally in the depth direction (sub-scanning direction) of the printer 1 along the surface of the left side frame 7. More specifically, guide pins 41a and 41b are provided on the left side frame 7, and long holes 52a and 52b extending horizontally in the front view are formed in the slide member 51, and the guide pins 41a and 41b are provided in these holes. Since the slide member 51 is attached so as to be loosely inserted, the slide member 51 can slide horizontally.

  On the other hand, a rack 54 is formed on the lower surface of the slide member 51, and a pinion gear 55 meshes with the rack 54. Power is transmitted to the pinion gear 55 in the order of gears 58 and 57 (the gears 58 and 57 are integrally formed) and the gear 56. The gear 58 is engaged with a conveyance drive roller gear 59 attached to the shaft end of the conveyance drive roller shaft 21, and the gear 60 (see FIG. 6) is engaged with the conveyance drive roller gear 59. The gear 60 is formed integrally with a pulley 61, and an endless belt 62 is wound around the pulley 61 and a pinion gear 63 attached to the rotation shaft of the conveyance motor 40. Therefore, the rotational driving force of the conveying motor 40 is transmitted to the pinion gear 55 by the tooth wheel train (power transmission device) as described above, and is converted into the sliding operation of the sliding member 51, whereby the bush members 67 and 68 are moved. PG changes by rotating.

  Reference numerals 42 and 43 denote rotary encoders. Reference numeral 42 denotes a disk-like scale that rotates with the pulley 61 and has a plurality of slits on the outer periphery. Reference numeral 43 denotes a light beam that passes through the slits of the disk-like scale 43. A light emitting unit that emits light, and a light receiving unit that receives the emitted light. The rotary encoder is connected to a control unit of the printer 1 (not shown), and can detect the rotation amount of the pulley 61, that is, the rotation amount of the transport driving roller 21 and the rotation amount of the gears constituting the gap adjusting device 50 in units of steps. it can.

  Next, the position of PG (gap position) and the holding means will be described. As shown in FIG. 9, the cam groove 53 into which the boss 65c is loosely inserted includes flat portions 53a, 53b, 53c as “non-change portions” of PG, and inclined portions as “change portions” of PG. It has a staircase shape. Here, the boss 65c rotates the intermediate gear 65 by moving the inclined portion, and does not rotate the intermediate gear 65 at the flat portions 53a, 53b, and 53c. Accordingly, the flat portions 53a, 53b, and 53c are non-change portions that do not change the PG, and are places where the PG can be held constant even if the slide member 51 slides slightly. And the gap adjustment apparatus 50 has three PG positions by three flat part 53a, 53b, 53c, and switches these in steps.

  In the present embodiment, as a means for holding the PG, a lock means for restraining the sliding operation of the slide member 51 is used. The lock means holds the PG by restricting the rotation of the pinion gear 55 a that meshes with the rack 54 formed on the slide member 51. Hereinafter, the slide member locking means for restricting the sliding operation of the slide member 51 by restricting the rotation of the pinion gear 55a will be described in detail.

  The pinion gear 55a has such a relationship that it protrudes from an annular hole 76 (see FIGS. 5 and 9) formed in the left side frame 7 toward the main scanning area of the carriage 13 (right side of the left side frame 7). Engaging projections 55a, 77b, 77c (details will be described later) that can be fitted in the corresponding fitting pins 55a and are formed on the left side frame 7 so as to correspond to the respective PG positions. 55b and 55c are formed on the disk surface facing the left side frame 7.

  Here, the pinion gear 55a is provided so as to be rotatable about the shaft 74 as a rotation shaft, and is provided to be slidable in the axial direction of the shaft 74. Further, the pinion gear 55a is directed toward the left side frame 7 by the biasing member 73. Is provided in an energized state. The sliding motion of the pinion gear 55 is performed by the urging member 73 and the carriage 13. That is, the engaging pin 55a is provided so as to be engageable with the carriage 13. When the carriage 13 moves to the left side 7 side, the carriage 13 pushes the engaging pin 55a (hereinafter, the position of the carriage 13 is changed). The pinion gear 55 is slid in a direction away from the left side frame 7 against the urging force of the urging member 73.

  In a state where the carriage 13 is not engaged with the engagement pin 55 a, the pinion gear 55 is in pressure contact with the side frame left 7 by the urging force of the urging member 73. At this time, the projections 55b and 55c are fitted into fitting holes 77b and 77b formed on the left side frame 7 as shown in FIG. 9, for example, so that the rotation of the pinion gear 55 is constrained. Therefore, the sliding operation of the slide member 51 is restrained and the PG is held. This is a locking means for the slide member 51. Further, in the locked state, the engagement between the pinion gear 55 and the gear 56 is released, that is, the pinion gear 55 is disengaged from the series of tooth wheel trains so that power is not transmitted.

  On the other hand, when the carriage 13 pushes the engagement pin 55a, the pinion gear 55 slides away from the left side frame 7 and is engaged with the gear 56. At this time, the protrusions 55b and 55c do not fit into any of the fitting holes (77a, 77b, 77c) formed in the left side frame 7, so that the protrusions 55b and 55c can rotate. After the pinion gear 55 is once removed from the positions of the fitting holes 77a, 77b, 77c, the protrusions 55b, 55c are pressed against the frame surface of the left side frame 7 even if the carriage 13 is separated from the left side frame 7. While sliding, it eventually fits into any of the fitting holes 77a, 77b, 77c and becomes locked, and the pinion gear 55 is disengaged from the tooth wheel train and does not transmit power.

  The tooth thickness of the rack 54 is formed thick so that the pinion gear 55 and the rack 54 are always engaged regardless of the sliding operation of the pinion gear 55. Similarly to the pinion gear 55, the gear 56 that meshes with the pinion gear 55 is provided so as to be slidable in the rotation axis direction, and is urged toward the left side frame 7 by the urging member 72 (FIG. 5). Yes. Therefore, when the pinion gear 55 is pushed by the carriage 13, even if the pinion gear 55 and the gear 56 are not engaged with each other, the gear 56 can be temporarily retracted in the direction away from the left side frame 7, and thereafter The pinion gear 55 and the gear 56 are normally meshed by the rotation. Therefore, damage to the teeth of the pinion gear 55 and the gear 56 can be prevented.

  By the way, although the number of engaging pins 55a formed on the pinion gear 56 is one in the present embodiment, when two or more engaging pins 55a are formed across the rotating shaft 74, the rotating shaft 74 is slid. A force parallel to the rotation shaft 74 is applied, so that the rotation shaft 74 can be slid more smoothly.

Hereinafter, the PG switching control sequence will be described in detail with reference to FIGS. 12 to 15 and other drawings as appropriate.
In FIG. 12, when performing the PG switching operation, the carriage 13 is moved to the PG switching standby position (step S101). The PG switching standby position is a position that is not engaged with the engaging pin 55a but is close to the engaging pin 55a, or is engaged with the engaging pin 55a, but has not yet pressed the engaging pin 55a. 13 positions.

  Next, it is determined whether the recording mode to be recorded is “PG ++”, “PG +”, or “PG0” (step S102), and the respective switching sequences are executed (steps S200, S300, S400). Here, “PG ++” is the largest PG, and is a PG when recording on the disk tray 33 described above. Further, “PG +” is an intermediate PG, and is a PG when recording on plain paper or the like. Furthermore, “PG0” is the smallest PG, and is a PG when recording is performed on dedicated paper or the like having a coating layer. Note that the PG for recording on plain paper is larger than the PG for recording on dedicated paper having a coat layer. The so-called cockling phenomenon in which plain paper absorbs ink droplets and undulates in the main scanning direction is remarkable. This is because the apparent thickness increases, and in some cases, the recording head 14 may be rubbed.

  Hereinafter, each switching sequence will be described. In the PG ++ switching sequence 200 shown in FIG. 13, first, it is determined which PG is the current PG (step S201). If the PG ++ is already in the “PG ++” state, no particular processing is performed and the upper control is performed. Return to the routine. Here, FIG. 11 shows a state in which the gap adjusting device 50 is “PG ++”, and in this state, the slide member 51 slides to the leftmost in a front view. Further, the boss 65c in the cam groove 53 is positioned at the uppermost flat portion 53c, and the projections 55b and 55c formed on the pinion gear 55 are fitted in the fitting holes 77a and 77a. 9 to 11 are diagrams around the rotation shaft 74 when the gap adjusting device 50 is viewed from the back side (the perspective view of FIG. 7 is a plan view).

  Next, if the current PG is “PG +” (the state shown in FIG. 10), the carriage 13 is moved to the pressing position (step S202), the conveyance motor 40 is reversed by β steps (step S203), and the carriage is moved. 13 is returned to the PG switching standby position (step S206). Here, in the lower right diagram in FIG. 10, the protrusions 55 b and 55 c are rotated in the counterclockwise direction in the drawing by the reverse operation of the transport motor 40. Further, it is assumed that the conveyance motor 40 rotates by β steps so that the protrusion 55c reaches the position of the fitting hole 77a one level higher than the state of FIG. Similarly, it is assumed that the protrusion 55c is rotated by α step to reach the position of the fitting hole 77c one lower than the fitting hole 77b.

  As described above, the slide member 51 slides to the left from the state shown in FIG. 10, and the boss 65c in the cam groove 53 moves from the intermediate flat portion 53b to the flat portion 53c one level higher, and further to the pinion gear 55. The formed protrusions 55b and 55c are moved from the fitting holes 77b and 77b to the fitting holes 77a and 77a to be fitted (state shown in FIG. 11).

  Returning to FIG. 13, if the current PG is “PG0” (the state shown in FIG. 9), the carriage 13 is moved to the pressing position (step S204), and the transport motor 40 is reversed by α + β steps (step S205). . As a result, the slide member 51 slides to the left from the state shown in FIG. 9, and the boss 65c in the cam groove 53 moves from the lowest flat part 53a to the two upper flat parts 53c, and further the pinion gear 55. The protrusions 55b and 55c formed in the state move from the fitting holes 77c and 77c to the fitting holes 77a and 77a to be fitted.

  Subsequently, in the PG + switching sequence 300 shown in FIG. 14, first, it is determined which PG is the current PG (step S301). If the PG + is already in the “PG +” state, no particular processing is performed. Return to upper control routine. Next, if the current PG is “PG ++”, the carriage 13 is moved to the pressing position (step S302), the conveyance motor 40 is rotated forward by β step (step S303), and the carriage 13 is moved to the PG switching standby position. (Step S306). Accordingly, the state of “PG ++” shown in FIG. 11 is changed to the state of “PG ++” shown in FIG.

  On the other hand, if the current PG is “PG0”, the carriage 13 is moved to the pressing position (step S304), the conveying motor 40 is reversed by α step (step S305), and the carriage 13 is returned to the PG switching standby position. (Step S306). As a result, the state of “PG0” shown in FIG. 9 is changed to the state of “PG +” shown in FIG.

  Furthermore, in the PG0 switching sequence 400 shown in FIG. 15, first, it is determined which PG is the current PG (step S401). Return to the control routine. Next, if the current PG is “PG ++”, the carriage 13 is moved to the pressing position (step S402), the conveyance motor 40 is rotated forward by α + β steps (step S403), and the carriage 13 is moved to the PG switching standby position. (Step S406). As a result, the state of “PG ++” shown in FIG. 11 is changed to the state of “PG0” shown in FIG.

  On the other hand, if the current PG is “PG +”, the carriage 13 is moved to the pressing position (step S404), the conveyance motor 40 is rotated forward by α step (step S405), and the carriage 13 is moved to the PG switching standby position. Return (step S406). As a result, the state of “PG +” shown in FIG. 10 is changed to the state of “PG0” shown in FIG. As described above, the gap adjusting device 50 is configured to switch the PG step by step to three stages of “PG ++”, “PG +”, and “PG0”.

  In the embodiment described above, the position of each PG is detected by the number of rotation steps of the conveyance motor 40 (number of detection steps of the rotary encoder). However, sensors 71 and 72 as shown in FIG. You may comprise so that the position of each PG may be detected by detecting the slide position of the member 51.

  By the way, in the gap adjusting device 50 configured as described above, the weights of the main carriage guide shaft 11, the sub carriage guide shaft 12 and the carriage 13 act on the bush members 11, 12. In view (in FIGS. 9 to 11), there is a force that tries to rotate clockwise. This force is transmitted to the boss 65c via the intermediate gear 65 (the intermediate gear 65 attempts to rotate counterclockwise in FIGS. 9 to 11), so that the boss 65c is positioned below the cam groove 53. The cam groove 53 is displaced in a state where it is always in pressure contact with the cam surface.

  Here, the press-contact direction of the boss 65c is a direction (a direction substantially orthogonal in the present embodiment) that intersects the slide direction of the slide member 51 (the horizontal direction in FIGS. 9 to 11). The weights of the carriage guide shaft 12 and the carriage 13 do not directly act on the conveying motor 40 via the toothed wheel train, and the PG can be adjusted with a small rotational torque. In this embodiment, the tension spring 66 is interposed between the intermediate gear 65 and the left side frame 7 so that the boss 65c does not bounce in the cam groove 53 (so that PG does not slightly change at each PG position). , And the boss 65c is always in contact with the lower cam surface of the cam groove 53. However, there is almost no influence by this, and the PG can be adjusted with a small rotational torque.

  With the above configuration, the gap adjusting device 50 can automatically switch the PG to a plurality of positions (three in this embodiment) using the driving force of the transport motor 40. In the present embodiment, three PG positions are set. However, the present invention is not limited to this, and it is needless to say that a plurality of PG positions can be set. In the present embodiment, the boss 65c is pressed against the lower cam surface of the cam groove 53. However, the boss 65c may be pressed against the upper cam surface.

  Further, as another embodiment of the present invention, in addition to the above-described one embodiment, the “bush member rotating member” is loosely inserted into the cam groove 53 in the entire rotation range of the intermediate gear 65. The slide member 51 is provided with a “deflection restricting means” for restricting the bending of the intermediate gear 65 in the direction in which the boss portion 65 c is removed from the cam groove 53 and preventing the boss portion 65 c from dropping from the cam groove 53. The provided gap adjusting device 50 is mentioned. As still another embodiment, the bush member 67 and the bush member 68 are biased in the rotational direction biased by the weights of the carriage 13, the main carriage guide shaft 11, and the sub carriage guide shaft 12. For example, the gap adjusting device 50 provided with a biasing means. Hereinafter, the “bending restricting means” and the “bush member biasing means” will be described with reference to FIGS. 16 to 20.

  FIG. 16 is a perspective view of an essential part of the gap adjusting device 50 according to the present invention. FIG. 17 is a side view of the main part of the gap adjusting device 50 according to the present invention, showing a cross section of the slide member 51. FIG. 18 is a front view of an essential part showing the gap adjusting device 50 according to the present invention from the back side.

First, in the entire range in which the intermediate gear 65 can be rotated, the boss portion 65c loosely inserted in the cam groove 53 is restricted from bending in the direction in which the intermediate gear 65 falls off the cam groove 53, and the boss portion 65c. The “bending restricting means” that prevents the cam from dropping from the cam groove 53 will be described.
When the boss 65c of the intermediate gear 65 is displaced in the cam groove 53 by the sliding operation of the slide member 51 and the intermediate gear 65 rotates, the inner wall of the cam groove 53 with which the boss 65c is in contact is the boss. By pushing 65c, the boss 65c is displaced along the shape of the cam groove 53 while slidingly contacting the inner wall of the cam groove 53. At that time, the inner wall of the cam groove 53 with which the boss 65c abuts pushes the boss 65c, so that the intermediate gear 65 is bent in the direction in which the boss 65c loosely inserted into the cam groove 53 falls off. A force acts on the intermediate gear 65. For this reason, if the intermediate gear 65 is greatly bent by the force, the boss portion 65 c may fall off the cam groove 53.

  In order to prevent the boss portion 65c loosely inserted into the cam groove 53, the slide member 51 is loosely inserted into the cam groove 53 in the entire range in which the intermediate gear 65 can be rotated. A guide wall 511 is formed as a “deflection restricting means” that restricts the bending of the intermediate gear 65 in the direction in which the boss 65 c drops from the cam groove 53. The guide wall 511 is formed along the cam groove 53 as shown in the figure, and the vicinity of the boss 65c of the intermediate gear 65 (the portion indicated by reference numeral 651) abuts to displace the boss 65c in the cam groove 53. The boss 65c loosely inserted in the cam groove 53 in a possible state restricts the bending of the intermediate gear 65 in the direction in which the boss 65c is dropped from the cam groove 53. By restricting the bending of the intermediate gear 65 in the direction in which the boss portion 65 c drops from the cam groove 53, the boss portion 65 c of the intermediate gear 65 is displaced in the cam groove 53 by the sliding operation of the slide member 51, and the intermediate gear 65. , The intermediate gear 65 can be prevented from being greatly bent and the boss portion 65c loosely inserted into the cam groove 53 from falling off the cam groove 53.

Next, the “bush member biasing means” that biases the bush member 67 and the bush member 68 in the rotational direction biased by the weights of the carriage 13, the main carriage guide shaft 11, and the sub carriage guide shaft 12 will be described. .
The “bush member urging means” includes a coil spring 78 that urges the bush member 67 in the rotation direction (reference A2) of the bush member 67 that is urged by the weight of the carriage 13 and the main carriage guide shaft 11, and the carriage. 13 and a coil spring 79 that urges the bush member 68 in the rotational direction (reference numeral B2) of the bush member 68 that is urged by its own weight. As described above, the gap adjusting device 50 is left with the axis C ₂ of the bush member 68 in front view rotation center C ₁ by-carriage guide shaft 11 (bushing member 67) (main carriage guide shaft 12) The sub-carriage guide shaft 11 (main carriage guide shaft 12) and the weight of the carriage 13 (reference numeral H in FIG. 18) act on the bush member 68 (bush member 67). The force which rotates in the rotation direction shown by code | symbol B2 (code | symbol A2) acts (refer FIG. 8). The coil spring 78 has one end (the portion indicated by reference numeral 781) hooked on the convex portion 671 formed on the bush member 67, and the other end (the portion indicated by reference numeral 782) is the base side of the ink jet printer 1. It is extended in a state of being fixed to (not shown). The spring force (symbol A1) of the coil spring 78 is the bushing member 67 that urges the bush member 67 in the rotational direction indicated by the symbol A2, that is, the weight of the carriage 13 and the main carriage guide shaft 11 (symbol H). Acting in the direction of rotation. The coil spring 79 has one end (portion denoted by reference numeral 791) hooked on a convex portion 681 formed on the bush member 68, and the other end (portion denoted by reference symbol 792) is on the base side of the ink jet printer 1. It is extended in a state of being fixed to (not shown). The spring force (symbol B1) of the coil spring 79 is the bushing member 68 that urges the bush member 68 in the rotating direction indicated by the symbol B2, that is, the weight of the carriage 13 and the sub-carriage guide shaft 12 (symbol H). Acting in the direction of rotation. The spring force (symbol A1) of the coil spring 78 acts in the rotation direction indicated by the symbol A3 of the intermediate gear 65 via the bush member 67, and the spring force (symbol B1) of the coil spring 79 is applied to the bush member 68. The intermediate gear 65 acts in the direction of rotation indicated by reference numeral B3.

  FIG. 19 is a front view of a main part of the gap adjusting device 50 according to the present invention, and shows a state where PG is “PG ++”. FIG. 20 is a front view of an essential part of the gap adjusting device 50 according to the present invention, and shows a state where PG is “PG0”.

  When the slide member 51 is slid in the direction indicated by symbol E from the state where PG is “PG ++” (the state shown in FIG. 19) (see FIG. 20), the boss portion 56 c of the intermediate gear 65 becomes the shape of the cam groove 53. Along the direction indicated by the reference symbol F, and thereby the intermediate gear 65 rotates in the rotational direction indicated by the reference symbol G. The bush member 67 is rotated in the direction indicated by symbol A2 by the rotation of the gear portion 65a of the intermediate gear 65 (reference symbol A3), and the bush member 68 is rotated (reference symbol B3) of the gear portion 65b of the intermediate gear 65. Is rotated in the direction indicated by reference numeral B2, whereby the main carriage guide shaft 11 and the sub carriage guide shaft 12 are displaced, and PG is switched from "PG ++" to "PG0". As described above, in the gap adjusting device 50, the weights of the carriage 13, the main carriage guide shaft 11, and the sub carriage guide shaft 12 act on the boss portion 65 c via the bush member 67, the bush member 68, and the intermediate gear 65. As a result, the boss 65c is displaced in the cam groove 53 while slidably contacting the cam surface on one side of the cam groove 53 (the direction indicated by the symbol H) in the direction intersecting the sliding direction of the slide member 51. It is configured to do.

  The spring force (symbol A1) of the coil spring 78 acts in the rotational direction indicated by the symbol A3 of the intermediate gear 65 via the bush member 67, and the spring force (symbol B1) of the coil spring 79 is the bush member. 68, the boss portion 65c of the intermediate gear 65 acts on the weight of the carriage 13, the main carriage guide shaft 11, and the sub carriage guide shaft 12 by the “bush”. A force obtained by adding the spring force of the coil spring 78 and the coil spring 79 as a member urging means is pressed and slidably contacted with the cam surface on one side of the cam groove 53 in a direction intersecting the slide direction of the slide member 51. It will be. Accordingly, the displacement position of the boss portion 65c of the intermediate gear 65 that is loosely inserted in the cam groove 53 of the slide member 51 can be further stabilized, so that the boss portion 65c that is loosely inserted in the cam groove 53 The gap between the recording head 14 and the recording medium (recording paper P or disk D) defined by the displacement position can be set with higher accuracy. In particular, a great effect can be obtained in the inkjet printer 1 in which the weight of the carriage 13 is light with an off-carriage structure (a structure in which the ink cartridge is not mounted on the carriage).

  The bush member 67 and the gear engaging portion (the gear portion 65a and the gear portion 65b) of the bush member 68 and the intermediate gear 65 are coil springs due to their own weights of the carriage 13, the main carriage guide shaft 11, and the sub carriage guide shaft. The force obtained by adding the spring force of 78 and the coil spring 79 always acts in the rotation direction (rotation direction indicated by reference signs A2 and B2) due to the weight of the carriage 13, the main carriage guide shaft 11, and the sub carriage guide shaft. To do. Accordingly, backlash between the bush member 67 and the gear portion 65a of the intermediate gear 65 engaged with the gear and between the bush member 68 and the gear portion 65b of the intermediate gear 65 can be eliminated.

  The present invention is not limited to the above-described embodiments, and various modifications are possible within the scope of the invention described in the claims, and they are also included in the scope of the present invention. Needless to say.

  The present invention is applicable to a gap adjusting device that adjusts a gap between a recording head and a recording medium, and a recording device that includes the gap adjusting device. Further, the present invention can be used for a liquid ejecting apparatus.

1 is an external perspective view of a printer according to the present invention. 1 is a perspective view of an internal appearance of a printer according to the present invention. 1 is a schematic side sectional view of a printer according to the present invention. 1 is an external perspective view of a gap adjusting device according to the present invention. It is a disassembled perspective view of the gap adjustment apparatus which concerns on this invention. 1 is an external perspective view of a gap adjusting device according to the present invention. 1 is an external perspective view of a gap adjusting device according to the present invention. It is a figure which shows the relationship between a bush member and a carriage guide shaft. It is a front view of the gap adjusting device according to the present invention. It is a front view of the gap adjusting device according to the present invention. It is a front view of the gap adjusting device according to the present invention. It is a figure which shows the control flow at the time of PG switching. It is a figure which shows the control flow at the time of PG switching. It is a figure which shows the control flow at the time of PG switching. It is a figure which shows the control flow at the time of PG switching. It is a principal part perspective view of the gap adjustment apparatus which concerns on this invention. It is the principal part side view which showed the cross section of the gap adjustment apparatus which concerns on this invention. It is the principal part front view which showed the gap adjustment apparatus which concerns on this invention from the back side. It is a principal part front view of the gap adjustment apparatus 50 which concerns on this invention. It is a principal part front view of the gap adjustment apparatus 50 which concerns on this invention.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Inkjet printer, 3 Housing, 4 Lower chassis, 5 Main frame, 6 Side frame right, 7 Side frame left, 8 Front cover, 11 Main carriage guide axis, 12 Subcarriage guide axis, 13 Carriage, 14 Recording head, 15 Ink Cartridge unit, 16 ink cartridge, 17 unit retraction knob, 20 platen, 21 transport drive roller, 22 transport driven roller, 23 paper discharge drive roller, 24 paper discharge driven roller, 28 paper feed roller, 30 paper feed cassette, 31 hopper, 33 Disc tray, 40 Conveyor motor, 41a, 41b Guide pin, 42 Rotary encoder, 43 Disc scale, 50 Gap adjusting device, 51 Slide member, 52a, 52b Long hole, 53 Cam groove, 53a- 3c flat part, 54 rack, 55 pinion gear, 56-58 gear, 59 transport drive roller gear, 60 gear, 61 pulley, 62 endless belt, 63 pinion gear, 65 intermediate gear, 651 guide wall, 65a, 65b gear part, 65c Boss, 66 Tension coil spring, 67, 68 Bush member, 70, 71 Sensor, 72, 73 Biasing member, 74, 75 Rotating shaft, 76 hole, 77a, 77b, 77c Fitting hole, 78, 79 Coil spring , D disc, P recording paper

Claims (11)

In a recording apparatus comprising a carriage having a recording head for recording on a recording medium and a carriage guide shaft for guiding the carriage in the main scanning direction, the recording is performed by adjusting the height position of the carriage guide shaft. A gap adjusting device for adjusting a gap between a head and a recording medium,
A member that is attached to the shaft end of the carriage guide shaft, and is rotatably provided on a side frame that is erected perpendicular to the axial direction of the carriage guide shaft. The rotation center and the carriage guide shaft A bush member that pivotally supports the carriage guide shaft in a state in which the shaft core does not match
A bush member rotating means that engages with the bush member and rotates the bush member, and operates by receiving the power of a motor;
A slide member to which the bush member rotating means, for sliding movement along the surface of the side frame receiving power from the motor,
Slide member locking means for restraining the sliding movement of the slide member;
A bush member engaging portion that engages with the bush member, and a boss portion that is loosely inserted into a cam groove formed in the slide member, are provided so as to be rotatable, and the boss portion is provided according to a slide operation of the slide member. A bush member rotating member that rotates by displacing the inside of the cam groove, thereby rotating the bush member,
Due to the discrepancy between the axis of the bush member and the axis of the carriage guide shaft, the weights of the carriage and the carriage guide shaft act as a force for rotating the bush member rotating member via the bush member. The boss portion of the bush member rotating member is pressed against the cam surface on one side of the cam groove in a direction intersecting the sliding direction of the slide member by the rotating force. Gap adjustment device.   2. The slide member according to claim 1, wherein the slide member is configured such that the boss portion loosely inserted in the cam groove is detached from the cam groove in the entire range in which the bush member rotation member is rotatable. A gap adjusting device, comprising: a deflection regulating means for regulating the deflection of the member rotating member to prevent the boss portion from falling off the cam groove.   3. The bending restricting means according to claim 1, wherein the bending restricting means is loosely inserted into the cam groove in a state where the boss is displaceable in the cam groove in contact with the vicinity of the boss of the bush member rotating member. A gap adjusting device, characterized in that a guide wall is formed along the cam groove for restricting the bending of the bush member rotating member in a direction in which the boss portion is removed from the cam groove. The cam groove according to any one of claims 1 to 3, wherein the cam groove includes a change portion that changes the gap and a non-change portion that does not change the gap so that the gap can be adjusted stepwise to a plurality of gap positions. A gap adjusting device characterized by comprising a stepped shape. According to claim 4, wherein by providing three non-changing portion, wherein is configured to be able to switch to three stages gap, the gap adjusting device, characterized in that. 6. The structure according to claim 1, wherein the bush member rotating means includes a pinion gear that meshes with a rack formed on the slide member and a transmission gear that rotates by receiving the power of the motor. is provided with a gear train provided in the side frame, the slide member is operated slide by the rotation of the pinion gear,
One gear constituting the tooth wheel train is provided so as to be slidable in the rotation axis direction, and is configured to be able to disconnect from the tooth wheel train and cut off the power transmission of the motor.
An urging means for urging the one gear in a direction in which the one gear meshes with another gear;
The engagement pin provided on the one gear protrudes from the arc-shaped hole formed in the side frame and protrudes into the main scanning region of the carriage in the direction in which the one gear is detached from the tooth wheel train. It said carriage, Ru done by the gap adjusting device, characterized in that.   7. The gap adjusting device according to claim 6, wherein the motor is a conveyance motor that rotationally drives a conveyance roller that conveys a recording medium. The engagement protrusion formed on the disk surface of the one gear according to claim 6 or 7, wherein the slide member locking means includes:
The side frame formed the engaging projection is a fitting hole that is fitted, is configured to include a fitting hole which is formed in plurality localized in a plurality of gaps located where the position of the engaging protrusion, the A gap adjusting device. In any one of the preceding claims, wherein the carriage, both the in the sub-scanning direction Ru is guided by two of said carriage guide shaft that is provided at a predetermined interval, said bushing member rotating member, the same time Ru rotated two carriage guide shaft disposed between and the two said bushing member attached to the shaft end of the carriage guide shaft, a gap adjusting device, characterized in that. A carriage having a recording head for recording on a recording medium;
A carriage guide shaft for guiding the carriage in the main scanning direction;
A gap adjusting device that adjusts a gap between the recording head and a recording medium by adjusting a height position of the carriage guide shaft,
The recording apparatus according to claim 1, wherein the gap adjusting device is the gap adjusting device according to claim 1. A carriage including a liquid ejecting head for ejecting liquid onto the ejection target medium;
A carriage guide shaft for guiding the carriage in the main scanning direction;
A liquid ejecting apparatus comprising: a gap adjusting device that adjusts a gap between the liquid ejecting head and the ejected medium by adjusting a height position of the carriage guide shaft;
The gap adjusting device is a member attached to the shaft end of the carriage guide shaft, and is provided rotatably on a side frame that is erected perpendicular to the axial direction of the carriage guide shaft. A bush member that pivotally supports the carriage guide shaft in a state where the center and the axis of the carriage guide shaft do not coincide with each other;
A bush member rotating means that engages with the bush member and rotates the bush member, and operates by receiving the power of a motor;
A slide member to which the bush member rotating means, for sliding movement along the surface of the side frame receiving power from the motor,
Slide member locking means for restraining the sliding movement of the slide member;
A bush member engaging portion that engages with the bush member, and a boss portion that is loosely inserted into a cam groove formed in the slide member, are provided so as to be rotatable, and the boss portion is provided in accordance with a slide operation of the slide member. A bush member rotating member that rotates by displacing the inside of the cam groove, thereby rotating the bush member,
Due to the discrepancy between the axis of the bush member and the axis of the carriage guide shaft, the weights of the carriage and the carriage guide shaft act as a force for rotating the bush member rotating member via the bush member. The boss portion of the bush member rotating member is pressed against the cam surface on one side of the cam groove in a direction intersecting the sliding direction of the slide member by the rotating force. Liquid ejector.

Images