Source: http://patents.com/us-7325895.html
Timestamp: 2019-06-20 07:35:56
Document Index: 560904031

Matched Legal Cases: ['art 44', 'art 44', 'art 44', 'art 44', 'art 44', 'art 44', 'art 44', 'art 44', 'art 44', 'art 44', 'art 44', 'art 44', 'art 44', 'art 44']

US Patent # 7,325,895. Printer - Patents.com
United States Patent 7,325,895
Nakashima February 5, 2008
Inventors: Nakashima; Atsuhisa (Nagoya, JP)
Appl. No.: 11/089,148
Mar 26, 2004 [JP] 2004-091062
Current International Class: B41J 25/308 (20060101)
Field of Search: 347/8
4620807 November 1986 Polit
5274399 December 1993 Uchida et al.
6343787 February 2002 Kato et al.
6799011 September 2004 Abe et al.
2003/0052957 March 2003 Yamada et al.
2003/0118388 June 2003 Sampson et al.
2005/0140723 June 2005 Taira
A 1 0 705 707 Apr., 1996 EP
A 2003-094744 Apr., 2003 JP
A printer of the present invention comprises a printing head, a pair of rollers, a carrier belt, and a moving mechanism. The printing head prints characters or images on a sheet opposing the printing head, and is typically an ink jet head, but could also be a thermal printing head or a dot printing head. The carrier belt is wound around the pair of rollers. The carrier belt sends the sheet to a printing position opposing the printing head, the sheet is printed at the printing position, and the carrier belt sends the printed sheet from the printing position. The moving mechanism shifts the pair of rollers by the same amount in a direction orthogonal to the delivery direction of the carrier belt. In the present specification, this process of shifting the pair of rollers is termed `changing the height` of the rollers. The moving mechanism may not only change the height of the rollers, but may simultaneously also move the rollers in the delivery direction of the carrier belt. As long as the moving mechanism shifts or moves the rollers in the direction orthogonal to the delivery direction of the carrier belt (that is, it changes the height of the rollers), the moving mechanism may simultaneously shift or move the carrier belt in the delivery direction. The moving mechanism changes the height of the pair of rollers by the same distance before and after the operation of the moving mechanism. It is not required to maintain the pair of rollers at the same height as always. Naturally, it is possible that the height of the rollers is maintained at the same height at every instance, and this is the preferred option.
FIGS. 6(a) and (b) show an operation of the driving system of the driving roller and the driving side moving mechanism. FIG. 6(a) shows the operation while the driving roller is rotating, and FIG. 6(b) shows the operation while the gap is being adjusted.
FIGS. 7(a) and (b) schematically show essential parts of a driven side moving mechanism. FIG. 7 (a) shows a state where a second cam member has been raised, and FIG. 7(b) shows a state where the second cam member has been lowered.
FIGS. 9(a) and (b) show an operation of the cam shaft and the cam shaft supporting member while adjusting a degree of parallelization. FIG. 9(a) shows a state where the cam shaft has been raised, and FIG. 9(b) shows a state where the cam shaft has been lowered.
An ink discharging face 2a is formed at a lower face of each of ink jet heads 2. A plurality of nozzles (not shown) is formed in each of the ink discharging faces 2a. Ink is discharged from each nozzle. The paper passing below the ink discharging faces 2a is printed by discharging ink from the nozzles. The paper is in a printing position when facing or opposing the ink discharging faces 2a.
The carrier unit 3 is assembled in the belt chassis 10. The belt chassis 10 has a pair of plates disposed in an orthogonal manner with respect to the page of FIG. 1. Driving roller 11 is provided at a left side of the belt chassis 10 between the pair of plates for forming the belt chassis 10. The driving roller 11 is supported by the belt chassis 10 such that the driving roller 11 can rotate freely with respect to the belt chassis 10. Driven roller 12 is provided at a right side of the belt chassis 10 between the pair of plates for forming the belt chassis 10. The driven roller 12 is supported by the belt chassis 10 such that the driven roller 12 can rotate freely with respect to the belt chassis 10. The driving roller 11 and the driven roller 12 extend between the pair of plats for forming the belt chassis 10.
First, a mechanism to deliver the carrier belt 13 will be described As shown in FIGS. 3, 4, and 5, a rotary shaft 11a of the driving roller 11 is supported such that it can be rotated with respect to the belt chassis 10 by means of a first cam member 43 (to be described). As shown in FIG. 4, the first cam member 43 has two cylindrical portions 43a, 43c and has a central hole 43b. The cylindrical portion 43a is supported by the belt chassis 10 and the cylindrical portions 43c is supported by the main chassis 10. The center of the cylindrical portions 43a is offset from the center of the cylindrical portions 43c by a distance d1. The rotary shaft 11a of the driving roller 11 is inserted into the central hole 43b. The central hole 43b is located at the center of the cylindrical portion 43a.
A pulley 21 is fixed to an end of the rotary shaft 11a of the driving roller 11. As shown in FIG. 3, a pulley 24a is fixed to a rotary shaft of a stepping motor 24 used for driving. A carrier belt 22 is wound across the pulleys 21 and 24a. A pulley 20 applies tension to the carrier belt 22. The stepping motor 24 used for driving is fixed to the main chassis 30. When the stepping motor 24 rotates, the driving roller 11 rotates, the carrier belt 13 is delivered, and the paper mounted on the carrier belt 13 is delivered towards the left relative to the left-right direction of FIG. 1. The driven roller 12 rotates following the delivery of the carrier belt 13.
The paper is delivered from right to left relative to FIG. 1 through a space (a gap) between the ink discharging faces 2a of the ink jet heads 2 and the carrier belt 13. The ink jet printer 1 is capable of printing on sheets of paper of varying thickness, such as plain paper, photographic paper, thick paper or envelopes, etc. It is preferred that there is a short distance from the ink discharging faces 2a to a surface of the paper when the paper is thin, so as to increase the accuracy of impact of the ink discharged from the nozzles. This is also the case for printing high quality images on photographic paper, etc. However, for printing plain paper or the like, there is no need for the gap to be narrow when particularly high quality printing is not required. Conversely, it is difficult to deliver the paper in a stable manner if the gap between the ink discharging faces 2a and the carrier belt 13 is too narrow. In particular, the paper can readily become jammed when comparatively thick paper such as envelopes, etc. is used.
To deal with this, the ink jet printer 1 is provided with a moving mechanism 40 for adjusting the gap between the ink discharging faces 2a of the ink jet heads 2 and the carrier belt 13.
The ink jet heads 2 are fixed to the main chassis 30. Consequently, the gap between the ink discharging faces 2a of the ink jet heads 2 and the carrier belt 13 is adjusted when the driving roller 11 and the belt chassis 10 at the side of the driven roller 12 are raised or lowered with respect to the main chassis 30.
As shown in FIG. 4, the first cam member 43 is formed from two overlapping cylindrical portions 43a and 43c, and the centers of the two cylindrical portions 43a and 43c are mutually offset by a distance d1. A hole 43b is formed at a center of the first cylindrical portion 43a, and passes through the second cylindrical portion 43c at a location offset from its center by the distance d1. The rotary shaft 11a of the driving roller 11 passes through the hole 43b.
The first cylindrical portion 43a is supported such that it can be rotated with respect to the belt chassis 10, and the second cylindrical portion 43c is supported such that it can be rotated with respect to the main chassis 30. As shown in FIGS. 4 and 5, cogs 43d are formed at an outer periphery of the cylindrical portion 43c of the first cam member 43.
As shown in FIG. 6(b), when the gear arm 37 rotates in an counterclockwise direction, the planet gear 36 engages with the cogs 43d at the outer periphery of the cylindrical portion 43c of the first cam member 43 (this will be described in detail later). Consequently, when the motor 24 rotates, the cylindrical portion 43c of the first cam member 43 rotates with respect to the main chassis 30. As described above, the rotational center of the driving roller 11 is offset by the distance d1 from the rotational center of the cylindrical portion 43c of the first cam member 43, with respect to the main chassis 30. When the cylindrical portion 43c of the first cam member 43 rotates with respect to the main chassis 30, the rotational center of the driving roller 11 moves along a circle having the radius d1 with respect to the main chassis 30.
A gear 44 engages with the cogs 43d formed at the outer periphery of the cylindrical portion 43c of the first cam member 43. The gear 44 at the further side, and a gear 44 at a closer side, relative to the plane of the page of FIG. 1, join with a shaft member 45. Since the gears 44 and the shaft member 45 are fixed, the rotation of the gear 44 at the further side and the gear 44 at the closer side is synchronized. As a result, the first cam member 43 at the further side relative to the plane of the page of FIG. 1, and the first cam member 43 at the closer side, rotate with the same timing and to the same extent. The end of the driving roller 11 at the further side, and the end of the driving roller 11 at the closer side are consequently raised or lowered with the same timing and to the same extent.
This state is shown in FIG. 6(a). When an output pulley 24a of the driving motor rotates in the counterclockwise direction of FIG. 6, driving force of the driving motor 24 is transmitted to the driving roller 11 via the carrier belt 22, and the driving roller 11 is thus driven to rotate. By contrast, the planet gear 36 moves in a clockwise direction along the outer periphery of the sun gear 35, the planet gear 36 disengages from the first cam member 43, and the driving force of the driving motor 24 is not transmitted to the first cam member 43, so that the first cam member 43 is not rotated.
In the case where the driving roller 11 is raised or lowered, the driving motor 24 is rotated in the clockwise direction of FIG. 5. When the driving motor 24 is rotated in the clockwise direction of FIG. 5, the sun gear 35 rotates in the counterclockwise direction, the gear arm 37 rotates in the counterclockwise direction, and the planet gear 36 engages with the first cam member 43. As a result, the first cam member 43 is rotated by the driving motor 24, and the rotary shaft 11a of the driving roller 11 moves upwards or downwards. In this case, the driving roller 11 rotates in the clockwise direction, and the upper side of the carrier belt 13 is delivered from left to right. The paper is not present when the driving roller 11 is raised or lowered, and consequently it is not a problem that the carrier belt 13 is rotating in the reverse direction.
This state is shown in FIG. 6(b). When the output pulley 24a of the driving motor rotates in the clockwise direction of FIG. 6, the planet gear 36 moves in the counterclockwise direction along the outer periphery of the sun gear 35, and the planet gear 36 engages with the first cam member 43. As a result, the driving force of the driving motor 24 is transmitted to the first cam member 43 via the gear 34, the sun gear 35, and the planet gear 36. Thereupon the first cam member 43 rotates, and the rotary shaft 11a of the driving roller 11 moves upwards or downwards.
The first cam member 43 is capable of rotating with respect to the rotary shaft 11a of the driving roller 11. Consequently, the first cam member 43 should not rotate even when the driving roller 11 is rotating. However, as shown in FIG. 4, the pulley 21 linked with the driving roller 11 is very close to one side of the first cam member 43. There is consequently a risk that, when the driving roller 11 is rotating so as to deliver paper, friction with the pulley 21 may drive the first cam member 43 to rotate. If the first cam member 43 is driven to rotate, the height of the driving roller 11 will be changed.
As described above, the gears 44 engage with the pair of first cam members 43 so as to cause the first cam members 43 to rotate in a synchronized manner. A protruding part 44a that protrudes inwards is formed at a portion of an inner face side (the left side in FIG. 4) of the gear 44. The main chassis 30 supports the shaft member 45, via a shaft supporting member 46, such that the shaft member 45 can rotate. The shaft supporting member 46 is fixed to the main chassis 30. Concave members 46a and 46b are formed in the shaft supporting member 46 at locations having point symmetry with respect to the shaft member 45, and the protruding part 44a can engage with these concave members 46a and 46b. Further, the shaft member 45 and the gear 44 are energized to the left, relative to FIG. 4, by a coiled spring 47. This locking structure is provided only at the side shown in FIG. 4.
When the rotary shaft 11a of the driving roller 11 is located in a raised state with respect to the main chassis 30 (in a state where the gap g1 is narrow), as shown in FIG. 1, the protruding part 44a is also in a raised position. The gear 44 is attracted towards the main chassis 30 by the energizing force of the coiled spring 47, and consequently the protruding part 44a engages with the upper concave member 46a, as shown in FIG. 4.
By contrast, when the rotary shaft 1a of the driving roller 11 is located in a lowered state with respect to the main chassis 30 (in a state where the gap g2 is wide), the protruding part 44a is also in a lowered position. In this case, the protruding part 44a engages with the lower concave member 46b.
The gear 44 cannot easily rotate when the protruding part 44a is engaged with the upper concave member 46a or the lower concave member 46b. Consequently, it is also difficult for the first cam member 43 to rotate. The protruding part 44a of the gear 44 engaging with the first cam member 43, and the concave members 46a and 46b fixed to the main chassis 30, function as a restraining mechanism. Frictional force with the pulley 21 is thus prevented from causing the rotation of the first cam member 43 when the driving roller 11 is rotating.
Moreover, the energizing force of the coiled spring 47 has a strength such that the engagement of the protruding part 44a and the concave members 46a and 46b is not easily released due to the frictional force between the first cam member 43 and the pulley 21. Moreover, the energizing force of the coiled spring 47 is set to a strength such that, when the first cam member 43 is being rotated, rotational resistance of the first cam member 43 does not become too great--this rotational resistance being caused by the engagement of the protruding part 44a and the concave members 46a and 46b.
As shown in FIG. 5, a notch-shaped detected part 44b is formed in the gear 44 that engages with the first cam member 43. By detecting the detected part 44b by using, for example, an optical sensor 48, it is possible to detect a reference position of the first cam member 43, i.e., a reference position of the rotary shaft 11a of the driving roller 11. Further, the number of driving steps of the driving motor 24 can be amended using the reference position detected by the sensor 48, such that it is possible to cause the first cam member 43 to rotate a determined angle from the reference position, so that the height at which the rotary shaft 11a of the driving roller 11 is located (the gap at side of the driving roller 11) can be adjusted.
Changes in the height of the driving roller 11 can be regulated at multiple stages by increasing the number of concave members 46 that engage with the protruding part 44a.
Next, the driven side moving mechanism 42 will be described.
As shown in FIG. 3, the driven side moving mechanism 42 has a cam shaft 50 and a second cam member 51. The main chassis 30 supports the cam shaft 50 such that the cam shaft 50 can rotate with respect to the main chassis 30, at an upwards side (the ink jet head 2 side) from the carrier belt 13. The second cam member 51 has a cylindrical shape, and is fixed to the cam shaft 50 with a positional relationship such that the cam shaft 50 passes through the second cam member 51 at a position offset from the center of the second cam member 51 by the distance d1 (see FIGS. 7(a) and (b)).
As shown in FIG. 3, a pulley 55 is fixed to the cam shaft 50. A gear 53 is provided that engages with the first cam member 43 of the driving side moving mechanism 41 (see FIG. 5). The gear 53 has a pulley 53a that rotates integrally therewith A transmitting carrier belt 57 is wound across the pulley 53a and the pulley 55 that is fixed to the cam shaft 50. Pulleys 54 and 56 exert tension on the transmitting carrier belt 57. Due to the above, the second cam member 51 fixed to the cam shaft 50, and the first cam member 43 of the driving side moving mechanism 41, rotate with an identical rotation frequency. The pulleys 53a, 54, 55, and 56 are capable of rotating with respect to the main chassis 30. The gear 53 has a number of cogs such that, when the first cam member 43 has been rotated by means of the driving motor 24 when the gap is adjusted, the driving roller 11 and the driven roller 12 are raised or lowered by the same extent. As a result, a configuration is formed in which, when the gap is adjusted, the carrier belt 13 that is maintained by the belt chassis 10 is raised or lowered while always being supported in a parallel state with respect to the head faces 2a.
As shown in FIGS. 3 and 7, both ends of the cam shaft 50 are supported by the main chassis 30, via a shaft supporting member 52, such that the cam shaft 50 can rotate. The second cam member 51 is fixed to the cam shaft 50 at both sides of the cam shaft 50. FIG. 3 shows only the second cam member 51 and the shaft supporting member 52 at a closer side relative to the plane of the page. In fact, a second cam member 51 and a shaft supporting member 52 are also present at a further side relative to the plane of the page. As described above, a center of the second cam member 51 is off-center by the distance d1 from the central axis of the cam shaft 50. This distance d1 is identical with the distance d1 between the rotational center of the cylindrical portion 43c of the first cam member 43 and the rotational center 11a of the driving roller 11.
When the first cam member 43 is rotated by means of the driving motor 24, the cam shaft 50 and the second cam member 51 fixed to the cam shaft 50 also rotate in synchrony with the rotation of the first cam member 43. This alters the height of the lower edge of the second cam member 51. As shown in FIGS. 7(a) and (b), the height of the lower edge of the second cam member 51 can be raised or lowered between a position raised by the distance d1 from a reference height shown in FIG. 7(a), and a position lowered by the distance d1 from the reference height shown in FIG. 7(b). This is identical to the distance of upwards or downwards movement of the rotational center 11a of the driving roller 11. The height of the lower edge of the second cam member 51 is raised or lowered following the height of the rotational center 11a of the driving roller 11.
As shown in FIGS. 1 and 4, when the driving side moving mechanism 41 has raised the rotary shaft 11a of the driving roller 11 by the distance d1 with respect to the main chassis 30, the driven side moving mechanism 42 raises the right end of the belt chassis 10 by the distance d1 with respect to the main chassis 30, as shown in FIG. 7(a). When the driving side moving mechanism 41 has lowered the rotary shaft 11a of the driving roller 11 by the distance d1 with respect to the main chassis 30, as shown in FIG. 2, the driven side moving mechanism 42 lowers the right end of the belt chassis 10 by the distance d1 with respect to the main chassis 30, as shown in FIG. 7(b).
The driven side moving mechanism 42 has a parallel adjusting mechanism 60 for adjusting an upper face of the carrier belt 13 such that it becomes parallel to the ink discharging faces 2a of the eight ink jet heals 2.
As shown in FIGS. 7 and 8, a cylindrical portion 52a is formed in the shaft supporting member 52 that supports the cam shaft 50. The cylindrical portion 52a is supported in the main chassis 30 such that it can rotate. A shaft receiving hole 52c through which the cam shaft 50 passes is formed in the cylindrical portion 52a. In the state shown in FIG. 8, a rotational center of the shaft receiving hole 52c is off-center, in a horizontal direction, by a determined quantity d3 from a rotational center of the cylindrical portion 52a.
As shown in FIG. 8, a circular arc-shaped groove 52b is formed in an upper edge portion of the shaft supporting member 52. The circular arc-shaped groove 52b extends in the direction of rotation of the shaft supporting member 52. The circular arc-shaped groove 52b has the same center as the cylindrical portion 52a As shown in FIG. 3, a screw 61 is passed through the groove 52b, and the screw 61 is tightened to fix the shaft supporting member 52 to the main chassis 30. When the screw 61 is loosened, the shaft supporting member 52 utilizes the cylindrical portion 52a to swing, within a vertical plane, with respect to the main chassis 30.
As shown in FIG. 8, the rotational center of the cam shaft 50 is off-center, in a horizontal direction, by a determined quantity d3 with respect to the center of the cylindrical portion 52a of the shaft supporting member 52. Consequently, as shown in FIG. 9(a), when the shaft supporting member 52 is rotated in an counterclockwise direction with the cylindrical portion 52a serving as the center, the cam shaft 50 rises by a determined quantity d4. Conversely, as shown in FIG. 9 (b), when the shaft supporting member 52 is rotated in a clockwise direction, the cam shaft 50 is lowered by a determined quantity d5. In this manner, rotating the shaft supporting member 52 within a vertical plane enables the height (the position along a direction perpendicular to the head faces 2a) of the cam shaft 50 to be adjusted such that the height of the driving roller 11 and the height of the cam shaft 50 become identical. The carrier belt 13 can thus be adjusted so that it is parallel to the ink discharging faces 2a.
Further, as shown in FIGS. 1 and 2, a guide member 62 and a pressing roller 63 are axially supported in the cam shaft 50. The guide member 62 guides the paper to the ink jet heads 2, and the pressing roller 63 presses, from above, the paper that is being carried to the ink jet heads 2. The guide member 62 and the pressing roller 63 enable the paper to be carried smoothly to the ink jet heads 2. Further, since the guide member 62 and the pressing roller 63 are disposed at the periphery of the cam shaft 50, a more compact configuration of the ink jet printer 1 is possible.
The ink jet printer 1 is provided with a swinging mechanism 15 that swings the belt chassis 10 across a vertical plane with the rotary shaft 1a of the driving roller 11 as the center. When maintenance of the carrier unit 3 is required, or paper has jammed within the carrier unit 3, the swinging mechanism 15 is activated to move the carrier unit 3 away from the ink discharging faces 2a of the ink jet heads 2.
As shown in FIG. 1, the swinging mechanism 15 comprises a raising and lowering cam member 31, a protrusion 31a, a cam receiving member 32, etc. The raising and lowering cam member 31 is supported in the main chassis 30 such that it can rotate. The protrusion 31a is formed integrally with the raising and lowering cam member 31. The cam receiving member 32 is movable with respect to the belt chassis 10 in the vertical direction in FIG. 1. A stopper (not shown) is provided with the belt chassis 10, and the stopper prevents from the cam receiving member 32 lowering further with respect to the belts chassis 10. That is, when the cam receiving member 32 is lowered with respect to the main chassis 30, the cam receiving member 32 abuts the stopper, and lowers the belts chassis 10 with respect to the main chassis 30. The cam receiving member 32 has a cam groove 32a formed in its lower edge part. The protrusion 31a engages with the cam groove 32a.
When the raising and lowering cam member 31 and the protrusion 31a rotate with respect to the main chassis 30, the cam receiving member 32 is moved upward or downward with respect to the main chassis 30. The belt chassis 10 may be movable vertically with respect to the cam receiving member 32. The belt chassis 10 is pushed upward by the compression springs 25 with respect to the cam receiving member 32.
A motor (not shown) is linked with the raising and lowering cam member 31, and the motor rotates the raising and lowering cam member 31 with respect to the main chassis 30. The protrusion 31a, which protrudes in a cylindrical shape perpendicular to a face of the raising and lowering cam member 31 (a direction perpendicular to the face of the page of FIG. 1), is formed at a location that is removed, in a radial direction, from a rotational center of the raising and lowering cam member 31. When the raising and lowering cam member 31 rotates, the protrusion 31a moves along a concentric circle of the raising and lowering cam member 31. The lower edge part of the cam receiving member 32 has the cam groove 32a formed therein, this extending in the longitudinal direction of the belt chassis 10 (the left-right direction of FIG. 1). The protrusion 31a engages with the cam groove 32a.
When the raising and lowering cam member 31 rotates, and the protrusion 31a moves along the concentric circle of the raising and lowering cam member 31, the cam receiving member 32 changes its height with respect to the main chassis 10.
During printing, the upper face of the carrier belt 13 is maintained such that it has been swung to an angle parallel to the ink discharging faces 2a of the ink jet heads 2, as shown by the solid line in FIG. 1. In this position, the compression springs 25 push the belt chassis 10 upwards via the carrier belt receiving unit 14 with respect to the cam receiving member 32. Lower ends of the compression springs 25 are supported by the main chassis 30 through the cam receiving member 32, the protrusion 31a and the raising and lowering cam member 31. Since the belt chassis 10 is pushed upward with respect to the main chassis 30, the belt chassis 10 is lifted until the belt chassis 10 abuts the second cam member 51. The upper face of the carrier belt 13 is maintained such that it has been swung to an angle parallel to the ink discharging faces 2a of the ink jet heads 2. In the case where paper has jammed, or the like, the cam receiving member 32 is lowed by the rotation of the raising and lowering cam member 31. When the cam receiving member 32 is lowered, it abuts the stopper of the belt chassis 10 and the belt chassis 10 is lowered As a result, the belt chassis 10 is swung downwards, as shown by the dashed line in FIG. 1, thereby removing the carrier unit 3 from the ink discharging faces 2a of the ink jet heads 2. It is thus possible to remove the jammed paper.
A concave member 32b is formed in the cam groove 32a. The concave member 32b has a circular arc shape and an upper end thereof is concave. When the belt chassis 10 is in a horizontal state, the cylindrical protrusion 31a engages with the concave member 32b. The belt chassis 10 is supported by the raising and lowering cam member 31 via the protrusion 31a, this preventing the belt chassis 10 from rattling while the paper is being delivered. Further, a notch 31b is formed in an outer peripheral portion of the raising and lowering cam member 31 at a determined location along the circumference thereof. A sensor (not shown) attached at the main chassis 30 side of the ink jet printer 1 detects the notch 31b. This detection makes it possible to detect the angle of rotation of the raising and lowering cam member 31, i.e., the degree of swinging of the carrier unit 3.
First, in the case where the paper will be printed using the ink jet heads 2, the output pulley 24a of the driving motor 24 is rotated in the counterclockwise direction, the driving force of the driving motor 24 is transmitted to the driving roller 11 via the carrier belt 22, and the driving roller 11 is thus driven to rotate (see FIGS. 1, 5, and 6(a)). Thereupon, the carrier belt 13 wound across the driving roller 11 and the driven roller 12 moves, the carrier belt 13 delivers the paper to the ink jet heads 2 from the right side of FIG. 1, and ink is discharged to the paper from the ink jet heads 2. At this juncture, as shown in FIG. 4, the protruding part 44a formed on the gear 44 that engages with the first cam member 43, and the concave members 46a and 46b fixed to the main chassis 30, prevent the rotation of the first cam member 43 that is engaging with the rotary shaft 11a of the driving roller 11. Consequently, there is no change in the height of the driving roller 11 during its rotation (while delivering paper).
However, in the case where the type of paper being delivered makes it necessary to change the gap between the carrier belt 13 and the head faces 2a of the inkjet heads 2, the driving motor 24 rotates in a clockwise direction (see FIGS. 1, 5, and 6(b)). Thereupon, the driving force of the driving motor 24 is transmitted to the first cam member 43, and the first cam member 43 rotates. At this juncture, the rotary shaft 11a of the driving roller 11, which is off-center with respect to the rotation of the first cam member 43, moves upwards or downwards, thus allowing the gap at the driving roller 11 side to be adjusted.
Simultaneously, the driving force of the driving motor 24 is transmitted, via the gear 53, the transmitting carrier belt 57, etc., to the cam shaft 50 of the driven side moving mechanism 42. Thereupon, in synchrony with the rotation of the first cam member 43, the second cam member 51 fixed to the cam shaft 50 rotates, and the height of its lower edge changes. Since the belt chassis 10 is energized upwards by the plurality of compression springs 25, the second cam member 51 and the belt chassis 10 are constantly maintained in a contacting state. When the height of the lower edge of the second cam member 51 changes, the portion of the belt chassis 10 at side of the driven roller 12 follows this height change and moves upwards or downwards. Consequently, the gap at the driven roller 12 side is adjusted. At this juncture, the belt chassis 10 is raised or lowered while being maintained parallel to the ink discharging faces 2a, and the driving roller 11 and the driven roller 12 are maintained at the same height.
In the moving mechanism 40 described above, the driving side moving mechanism 41 raises or lowers a portion of the belt chassis 10 at the side of the driving roller 11, and in synchrony with the driving side moving mechanism 41, the driven side moving mechanism 42 raises or lowers a portion of the belt chassis 10 at the side of the driven roller. Consequently, the gap between the head faces 2a and the carrier belt 13 can be adjusted while the carrier belt 13 is being maintained in a parallel state with respect to the head 2a. As a result, printing quality can be improved, and paper can be delivered smoothly to the ink jet heads 2.
The motor for rotating the cam shaft 50 of the driven side moving mechanism 42 may equally well be different from the motor for rotating the first cam member 43 of the driving side moving mechanism 41 (the driving motor 24 in the embodiment described above), and the driving side moving mechanism 41 and the driven side moving mechanism 42 may be synchronized by means for electrically causing the synchronization of these two motors. Furthermore, the driving side moving mechanism 41 and the driven side moving mechanism 42 need not necessarily be made to operate in synchrony. For example, the driven side moving mechanism 42 can raise or lower the belt chassis 10 at the side of the driven roller 12 after the driving side moving mechanism 41 has raised or lowered the belt chassis 10 at the side of the driving roller. That is, it is equally possible for the carrier belt 13 to be made parallel to the head faces 2a at a final stage in adjusting the gap.
A pair of rollers 11, 12 is supported, such that they can rotate, in the belt chassis 10. It is preferred that the moving mechanism 40 is provided with two adjusting mechanisms 41 and 42. One of the adjusting mechanisms 41 changes the height of the rotary shaft 11a of one of the rollers. The other adjusting mechanism 42 changes the height, by the same distance, of an end of a belt chassis 10 at the side supporting the other roller 12.
In the case where one of the adjusting mechanisms 41 moves the rotary shaft 11a, and the other adjusting mechanism 42 moves the belt chassis 10, the movement of the two mechanism 41, 42 may be independent in the delivery direction, and the configuration of the moving mechanism 40 is thus simplified.
It is preferred that the moving mechanism 41 for shifting the rotary shaft 11a shifts the rotary shaft 1a of the driving roller 11 of the carrier belt 13. This makes it easier for the driving source for changing the height of the rotary shaft 11a of the driving roller 11 to also function as the driving source for driving the carrier belt 13.
It is preferred that a cylindrical portion 43c capable of being rotated with respect to the main chassis 30 supports the rotary shaft 11a of the driving roller 11, in a manner allowing rotation of the driving roller 11, at a location offset from a rotational center of the cylindrical portion 43c. In the present specification, the cylindrical portion 43c supporting the rotary shaft 11a of the driving roller 11 in this manner is turned the first cam member 43.
In this case, the height of the rotary shaft 11a of the driving roller 11 is changed when the first cam member 43 is rotated with respect to the main chassis 30.
The rotary shaft 11a of the driving roller 11 also moves in the delivery direction when the first cam member 43 is rotated with respect to the main chassis 30. If the mechanism for changing the height of the end of the belt chassis 10 at the side of the driven roller 12 does not restrict the movement of the belt chassis 10 in the delivery direction, there will be no inconsistent movement between the two sides.
It is preferred that a motor for rotating the first cam member 43 with respect to the main chassis 30 also functions as a motor causing the rotation of the rotary shaft 11a of the driving roller 11. The number of motors required can thus be reduced, and consequently the cost of manufacturing the printer 1 can be reduced.
It is preferred that a restraining mechanism 44a, 46a and 46b is provided that prohibits rotation of the first cam member 43 while the rotary shaft 11a of the driving roller 11 is rotating. This prevents a change of position of the driving roller 11 while the driving roller 11 is rotating so as to deliver the sheet.
It is preferred that the parallel adjusting mechanism 60 is provided between the main chassis 30 and the cam shaft 50. This parallel adjusting mechanism 60 is capable of changing the height of the cam shaft 50 with respect to the main chassis 30. It is thus easy to adjust the degree of parallelization of the carrier belt 13 with respect to a head face 2a.
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